Diploma - Heating, ventilation and air conditioning

Contents

WITH ABOUT D E P AND N AND E:

1. Source Data

1.1.The purpose and characteristics of the building

1.2. Climatic characteristics of the construction area

1.3.Computed ambient air parameters

1.4. Design parameters of internal air

1.5. Engineering Assignment for Design

2. Construction heat engineering

2.1.Determination of required heat transfer resistance of external enclosing structures

2.2. Heat Engineering Calculation of External Enclosures

2.2.1.Define the reduced heat transfer resistance of the outer wall and the thickness of the insulation layer

2.2.2.Determination of reduced heat transfer resistance of the floor

2.3.Select filling of window and door openings

2.4. Evaluation of humidity mode of external enclosures

2.4.1.Verifying the possibility of condensation of water vapors on the inner surface of the outer wall

2.4.2.Verifying the possibility of condensation of water vapors on the wall surface at the place of thermal connection

2.4.3.Verifying the possibility of condensation of water vapors in the outer wall

2.4.4. Inspection of enclosing structures for air permeability

2.5. Definition of thermal losses through enclosing structures

2.6. Determination of heat flow rate for heating of infiltrating outdoor air

3. Heating

3.1. Heating System Selection and Design

3.2.Hydraulic calculation of heating system

3.3.Construction and composition of heat station equipment

3.4.Heat calculation of heating devices

4. Ventilation and conditioning

4.1.Determination of heat, moisture and harmful emissions

4.2.Selection, description and calculation of funcoils

4.3. Determination of supply and exhaust air

4.4.Selection of ventilation and air conditioning system diagram

4.5. Calculation of air distribution

4.6.Aerodynamic calculation of air ducts

4.7. Selection of main equipment and design of plenum and exhaust plants

4.8Production of air treatment processes on i-d diagram

4.9. Anti-smoke measures

4.10.SmOoling Measures

4.10.1Compute the silencer

5. Cold supply

5.1.Chill supply of air conditioning system.885.

Cold Supply Schematic Diagram Description

5.3.Protection against icing of system components

5.3. Cold supply of funkoil. Hydraulic calculation

6. Data Center Precision Conditioning System

6.1.Compute required cooling capacity

6.2.Accepted process and design solutions

6.3.System control and automation

6.4. Organization of installation and commissioning works

6.4. Environmental protection and working substance characteristics

7. Technical and economic part

7.1.Technical-economic comparison of options

7.2.System Brief Description

7.3.Define Capital Costs for Equipment Purchase and Installation

7.4. Determination of annual operating costs

7.5. Determination of annual depreciation deductions

7.6. Determination of total reduced costs. Schedule. Conclusion

8. Automation

8.1. Description of the automation object

8.2.Availability of object automation and control

8.3.Accepted design and process solutions

8.4. Functional diagram of automation

9. Organization of works execution

9.1.Technology of work execution organization

9.2.Installation of the object for installation works

9.3.Installation Engineering

9.4.Installation of ventilation equipment

9.5.Defining Scope of Work and Costing

9.6. Installation tool for mechanization of installation works

9.7. Organization of work quality control

10. Occupational safety

10.1.Safety during installation of special structures

10.2. Ensuring safety of ventilation equipment installation

10.3.Safety of engineering works organization

10.4. Workplace Security Organization

10.5.Safety of engineering works

10.6.Security if people are to be evacuated from the building

11. List of sources used

ATTACHMENTS:

Appendix No. 1. Table of heat loss calculations

Appendix No. 2. Heating system control valves

Appendix No. 3. Hydraulic calculation of heating system

Appendix No. 4. Heating system balancing valve

Appendix No. 5. Hydraulic calculation of fancoil heat supply system pipelines

Appendix No. 6. Fancoil Heat Supply Balancing Valve

Appendix No. 7. Heat exchanger. Settlement form. Technical description

Appendix No. 8. Expansion tank calculation

Appendix No. 9. Heating Fixtures Calculation

Appendix No. 10. Heat Inputs to Rooms

Appendix No. 11. Idrofan 42N Funcoils Technical Description

Appendix No. 12. Calculation of air exchanges

Appendix No. 13. Aerodynamic calculation of ducts

Appendix No. 14. Calculation of smoke protection

Appendix No. 15. Hydraulic calculation of fancoil cold supply system pipelines

Appendix No. 16. Calculation of PCS cooling capacity

Appendix No. 17. Specification of PCS equipment and materials

Heating, ventilation and air conditioning of the regional branch office of the telecommunications company in Chimkent

Source Data

1.1. Purpose and characteristics of the building.

Purpose: Administrative building of the regional branch of the telecommunications company.

Construction district: South Kazakhstan region, Chimkent,

st. _ Baitursynova d.25a.

This building is a frame structure with filling with blocks of mesh-concrete blocks, consisting of 3 floors: basement, first and second floors.

On the basement floor there are office, technical rooms, electric panels, a ventilation chamber, a technological room of the Data Processing Center (DPC) and uninterrupted power supply rooms of the PSU, an archive and a control unit for heating, ventilation and hot water supply systems ..

On the ground floor there are classrooms for training and advanced training, conference halls, bathrooms, administrative and office rooms, and a meal room.

On the third floor there are two operating rooms representing an open-type office room with workplaces such as "Openspace," a rest and meal room, a dressing room, offices, and a switching room.

In plan view, the building has a rectangular section with dimensions in axes 73x15m.

The height of the floors from floor to floor is 3.3 m.

The height of the floors from floor level to ceiling is 3.0 m.

The construction area refers (according to SNiP 23022003 "Thermal protection of buildings" Appendix "B" - "Map of humidity zones") to the normal humidity zone. The building is maintained (as per SNiP 23022003 "Thermal protection of buildings," Table 1 "Humidity mode of buildings premises") - normal humidity mode

Orientation of the main facade of the building - North-West (SZ)

Humidity zone - dry

Humidity mode of rooms - normal,

Operating conditions - parameters A,

All floors of the building are heated .

1.2. Climatic characteristics of the construction area.

- design ambient air temperature (CP) for designing ventilation and air conditioning heating, coldest five-day coverage 0.98 - tH0,98 = - 17 ° C, coverage 0.92 - tH0,92 = - 15 ° C

- average temperature of heating period - top = 1.4 ° C

- the duration of the heating period is - zop. = 160 days..

- estimated wind speed for the cold period, as the maximum of the average speeds in rumbs for January - VChP = 2.5 m/s,

- average wind speed for the period with average daily air temperature ≤ 8 ° C is V = 2.4 m/s ,

- relative humidity (average monthly humidity for the coldest month) external air φН = 75%,

- average temperature of each month of the year:

- average elasticity of outdoor water vapor by months:

- average for the coldest month of the year (January) partial pressure of water vapor of eh. m = 4.0hPa = 400 Pa = 0.4 kPa .

- design ambient air temperature (TC) for air conditioning design - tH0,95 = + 33.6 ° C SNiP 230199 table.2

- average daily temperature amplitude of warmest month is AT = 15.2 ° C ,

- estimated wind speed for warm period of year V = 2.4 m/s

- calculated specific air enthalpy for warm period:

- by parameters A - I A.T = 66.5 kJ/kg; (By I-D-chart)

- in the B parameters B-I. T = 87.3 kJ/kg; (By I-D-chart)

- design barometric pressure is P = 1010 hPa.

1.3. Outside air design parameters

Other necessary data on outdoor air parameters are determined on the basis of Annex 8 of SNiP 2.04.0591 (2000) "Heating, ventilation and air conditioning" and using the I-d diagram for wet air:

1.4. Design parameters of internal air.

In accordance with SNiP 2.04.0591 (2000) "Heating, Ventilation and Air Conditioning," Annexes 1, 2.

Other necessary data on internal air parameters are determined on the basis of SNiP 2.04.0591 (2000) "Heating, ventilation and conditioning" and using the I-d diagram for wet air:

1.5. Engineering Terms of Reference.

"Technical assignment for the development of the building heating, ventilation and air conditioning design."

The heat supply source is the own existing boiler house.

Coolant temperature for heating and ventilation needs 9570 ° С,

for heating needs of fancoyles 70-60 ° С

Hot water is prepared in a separate boiler room.

The project shall provide in the building for:

1. Heating and cooling.

Heat and cold supply system shall be provided closed, through plate water heat exchanger, with forced circulation of heat and cold carrier.

Parameters of closed circuit coolant 8060 ° С.

Maintenance of comfortable parameters in office premises shall be carried out by the heat and cold supply system (TCS) using funcoils operating in two modes: as air heaters and internal air coolers, with air temperature adjustment.

The central equipment of ventilation, air conditioning and cold supply systems will be designed by CARRIER (USA).

Coolant parameters - water 712 ° С.

Central air conditioner heaters shall be connected directly from boiler room coolant.

Provide water heating with installation of radiators.

In the auxiliary rooms of the office part and bathrooms provide heating devices - radiators - of an improved design.

MS90 radiators and smooth tube registers shall be provided as heating devices of technical and process rooms.

Coolant for heating system - water with parameters 9070 ° С.

Distribution pipelines of heat and cold supply systems shall be provided with polypropylene, main heat supply pipelines - electric welded steel as per GOST 1070491, heating pipelines - water and gas pipelines as per GOST 326275. Heat supply pipelines and cold supply pipelines shall be insulated with tubular insulation.

2. To prevent the penetration of cold air into the building near the external doors, provide air-heat curtains.

3. Ventilation.

All rooms shall be provided with mechanical supply ventilation.

Air exchange in office premises shall be determined from the condition of sanitary norm supply, in auxiliary rooms of the building - by multiplicity.

Supply air treatment shall be performed in central air conditioners installed in the ventilation chamber.

Galvanized steel ducts shall be provided for distribution and removal of supply and exhaust air.

The project shall provide smoke ventilation. The air ducts of the smoke removal system shall be protected with a flame retardant coating.

Channel fans shall be installed for exhaust systems.

To prevent the propagation of noise through the air ducts, the supply system shall be provided with silencers.

When crossing fire barriers and floors, provide installation of fire retardant valves with electric drive.

4. Precision conditioning of the Data Processing Centre machine room.

The Precision Air Conditioning System shall provide optimum temperature and humidity conditions for switching, telecommunication, server, electrical and other process equipment located in the equipment room.

PCMS shall be autonomous, with N + 1 redundancy.

Steam humidifiers shall be provided to maintain humidity parameters within the room of the engine room. Supply water to the humidifier from existing cold water system risers and provide water quality acceptable for the equipment. Install water filters at the attachment point.

Condensate removal from internal units shall be provided to existing risers of sewage systems using drain pumps. Connect the drain pipeline to the sewer riser through the hydraulic seal.

To lay communications - on the street is open, in the room - under a false floor.

Install air-cooled units of outdoor system on the street. The installation location is defined by the project.

Provide additional linear receivers.

The type of air conditioners shall provide air circulation according to the principle of cold and hot corridors by air circulation at the level of telecommunication and server cabinets, and ensure uniform distribution of air conditioned air into the inter-row space.

The software and hardware of air conditioners control shall provide the functions of remote control of operation modes and monitoring of condition of air conditioners with visualization of its operation parameters.

Section 2

Construction heat engineering

2. Thermal and humidity calculation of building enclosing structures.

Heat engineering calculation is carried out to check compliance of the enclosing structure with the heat engineering requirements of SNiP II379 * "Construction heat engineering."

1. Determination of required heat transfer resistance of external enclosures.

The required heat transfer resistance based on sanitary and hygienic and comfortable conditions in the design cold period is determined by the formula:

n is a factor that takes into account the dependence of the position of the external surface of enclosing structures with respect to the external air (Given in Table 6 of SNiP 23022003 "Thermal protection of buildings"), n = 1.

ΔtH - normalized temperature difference between the temperature of internal air tB and the temperature of internal surface tV of the enclosing structure, ° С, (Table 5 SNiP 23022003 "Thermal protection of buildings"), ΔtH = 4.5 ° С for external walls, and 4.0 ° С for coatings.

αВ - coefficient of a thermolysis of an internal surface of enclosing structures, W / (м2× °C), (table 7 Construction Norms and Regulations 23022003 "Thermal protection of buildings"). For walls, floors and smooth floors = 8.7, for windows - 8.0.

tB - design internal air temperature GOST 3049496, tB = 20 ° С.

tH - design outside air temperature in the cold period of the year, ° С (the coldest five-day coverage is 0.92 according to SNiP 230199), tH = 17 ° С.

Thus, the required heat transfer resistance based on sanitary and hygienic conditions:

- for exterior wall and covering (without attic floor):

- for coating (without attic floor under roll roof):

- for inlet doors the required heat transfer resistance shall be, in accordance with item 5.7 of SNiP 23022003 "Thermal protection of buildings" not less than 0,6•RoTP external walls of buildings:

The required heat transfer resistance based on energy saving during the heating period is determined (Table 4. SNiP 23022003 "Thermal protection of buildings") for the functional purpose of the building - public and number of degrees of heating period equal to:

tB - design temperature of internal air - accepted as per GOST 3049496 "Residential and public buildings. Indoor microclimate parameters, "Table 2, for category 2 rooms, for cold period equal to 20 ° С.

pOS - heating period temperature, as per SNiP 230199 * "Construction climatology," Table 1., equal to 1.4 ° С.

zOP - duration of heating period, according to SNiP 230199 * "Construction climatology," Table 1., equal to 160 days.

Thus, taking into account interpolation (Table 4. SNiP 23022003) by the number of degrees, required heat transfer resistance:

- for exterior walls:

Also calculation of values that differ from table values (Table 4. SNiP 23022003 "Thermal protection of buildings") can be determined by the formula:

R0TP = a•Dd +b

where a, b are the coefficients to be taken from the table data for the respective building groups.

- for exterior walls:

- for slabs:

- for windows:

The required heat transfer resistance accepted for designing buildings with a design internal air temperature above 12 ° C is normalized based on energy saving. Thus, for further heat engineering calculation we accept:

- for external walls R0TP = 2.09 m2 ° C/W

- for slabs R0TP = 2.79 m2 ° C/W

- for R0TP = 0.34 m2 ° C/W windows

Heat engineering calculation of external enclosures.

1. Determination of the given heat transfer resistance of the outer wall and thickness of the insulation layer.

The multi-layer exterior enclosure for the three-storey office building is schematically shown in Fig. 2.1. "Exterior fence design. Wall. "

The construction area refers (according to SNiP 23022003 "Thermal protection of buildings" Appendix "B" - "Map of humidity zones") to the dry humidity zone.

The building is maintained (as per SNiP 23022003 "Thermal protection of buildings," Table 1 "Humidity mode of buildings premises") normal humidity mode .

Under normal humidity conditions of the room and dry humidity zone of the construction area, all fences of the facility are in operation conditions related to gradation "A."

Heat engineering indicators of construction materials (according to SP231012000 "Design of thermal protection of buildings", Appendix E (obligatory), Tab. E.1. "Normalized Heat Engineering Indicators of Construction Materials and Products" or SNiP II379 "Construction Heat Engineering, Appendix 3 *) are summarized in Table 2.1. "Heat engineering indicators of building materials of the outer wall."

The reduced heat transfer resistance is determined by the formula (according to SP231012000 "Design of thermal protection of buildings," item 6.1.4.) :

R0 = R0USL. r ,

where:

R0SL - conditional resistance to heat transfer of the structure without taking into account thermal conductive inclusions (connections), m2. ° C/W;

r is the coefficient of thermal uniformity of the wall. In this case, we take r = 0.9.

Taking R0 = R0TP = 2.09 (m2 ° C )/W, we obtain the required conditional heat transfer resistance of the smooth wall:

R0SL = 2.09/0.9 = 2.32 (m2 ° C )/W.

The heat transfer resistance of the outer wall, excluding the insulation layer, will thus be:

Ri = δi/αi - resistance to heat transfer of the outer fence layer,

αВ and αН thermolysis coefficient according to an internal and external surface of enclosing structures, W / (м2× °C), (table 7 Construction Norms and Regulations 23022003 "Thermal protection of buildings").

The obtained heat transfer resistance of the outer wall meets the requirements of sanitary and hygienic and comfortable conditions, but the required heat transfer resistance adopted for designing buildings with a design internal air temperature above 12 ° C is normalized based on energy saving .

Thus, at R0 ˂ R0TP, the wall structure needs to be insulated.

Thermal resistance of the insulation material will be:

RYT = R0SL - R0 = 2.32 - 0.96 = 1.4 (m2. ° C )/W.

Foam polystyrene is used as heat insulating material. As a result, according to SP231012000 Appendix E, we determine the material that has recently become widespread - foam polystyrene extrusion "Penoplex," type 35, (TU 576700246261013) with thermal characteristics:

- density ρ = 35 kg/m3,

- thermal conductivity coefficient under operating conditions A, γ = 0.029 W/( m2. ° C ),

- in vapor impermeability coefficient - µ = 0.018 mg / (m of h Pa)

Then the calculated thickness of the insulation layer will be :

We accept the thickness of the insulation - plate of extruded polystyrene - 60 mm. (one of the standard dimensions of the MPS plate indicators). We lay one layer of polystyrene on the outer surface of the outer wall before applying a layer of external plaster (1st layer).

Thus, the 1st layer will be a layer of external plaster 20 mm thick, the 2nd layer will be an insulating material from extruded polystyrene 60 mm thick, the 3rd layer will be a structural layer, of cellular concrete blocks 200 mm thick, the 4th layer will be an internal plaster 20 mm thick..

The heat transfer resistance of the outer wall will thus be:

Thus, in further design calculations we accept:

Reduced heat transfer resistance of the outer wall:

R0PR = R0USL. r = 3.1.0.87 = 2.72 m2 ° C/W.

Wall heat transfer coefficient:

KNS = 1/R0PR = 1/2.36 = 0.37 W / (sq.m. ° C).

2. Determination of the given heat transfer resistance of the floor.

The multi-layer exterior enclosure for the three-storey office building is schematically shown in Fig. 2.2. "Exterior fence design.

Heat engineering indicators of construction materials (according to SP231012000 "Design of thermal protection of buildings", Appendix E (obligatory), Tab. E.1. "Normalized Heat Engineering Indicators of Construction Materials and Products" or SNiP II379 "Construction Heat Engineering, Appendix 3 *) are summarized in Table 2.2. "Heat engineering indicators of building materials."

We will calculate the thermal resistance of the hollow reinforced concrete panel, which is carried out by the method of adding conductivities (as per SP231012000 "Design of thermal protection of buildings," item 6.1.8.) .

The dimensions of the panel and the voids in it are shown in the figure below:

a) section along the slab fragment,

b) design diagram of the plate with the selected regular element.

For calculation, we accept the section diagram of the plate with square instead of round holes in the wall. The side of the square equivalent in area (Aquadrata = Akruga) is equal to:

We highlight the regular element and divide it in planes parallel to the heat flow (see diagram of figure b)). We get two parallel sections: I and II. Section I is uniform, section II is non-uniform, consisting of two layers of the same thickness and an air layer.

Heat transfer resistances of these sections are equal to:

Thermal resistance of air interlayer R&VR is determined as per SP 231012004 "Design of thermal protection of buildings," Table 7 "Thermal resistance of closed air interlayers."

In view of the fact that in the floor panel the horizontal air layer with the heat flow from the bottom up is separated from the outside air by a layer of insulation, therefore the air in it is at a positive temperature. For a layer with a thickness of 0.14 m under these conditions, R/V = 0.15 (m2 • ° C )/W.

Then RII = 0.04 + RF = 0.04 + 0.15 = 0.19 m2 • ° C/W

Heat transfer resistance of the entire regular element when it is separated by planes parallel to the heat flow for the overlap:

Where AI and AII are areas of 1 m along the length of the I and II sections in the regular element of the plate, in m2.

We divide the regular element with planes perpendicular to the heat flow (see diagram on the right). We get three parallel sections: a, b, c.

Sections a and b are homogeneous, section b is inhomogeneous, consisting of a horizontal air layer and a layer of reinforced concrete, width - I and thickness - b. RG/B = 0.14/1.92 = 0.073 m2 • ° С/W

Heat transfer resistances of these sections are equal to:

Heat transfer resistance RB, defined (SNiP II379 *, formula (6)):

Heat transfer resistance of the entire regular element at its separation by planes perpendicular to the heat flow:

Thus, thermal resistance of reinforced concrete hollow slab (SNiP II379 *, formula (7)):

from here

Further, RG/B. PLATES = 0.152 (m2 • ° C )/W are used in the calculation.

The reduced heat transfer resistance is determined by the formula (according to SP231012000 "Design of thermal protection of buildings," item 6.1.4.) :

R0 = R0USL. r ,

where:

R0SL - conditional resistance to heat transfer of the structure without taking into account thermal conductive inclusions (connections), m2. ° C/W;

r - coefficient of thermal uniformity. In this case, we assume that r = 0.75. (SNiP II379 *, Table 6a *).

Assuming R0 = R0TP = 2.8 m2 ° C/W, we obtain the required conditional heat transfer resistance of the outer floor (without attic):

R0SL = 2.8/0.75 = 3.72 (m2 ° C )/W.

We determine the required value of heat transfer resistance of the insulation layer:

Thus, the structure of the fence (slab) must be insulated at RYT = 3.13 (m2. ° C )/W.

Foam polystyrene is used as heat insulating material. As a result, according to SP231012000 Appendix E, we determine the material that has recently become widespread - foam polystyrene extrusion "Penoplex," type 35, (TU 576700246261013) with thermal characteristics:

- density ρ = 35 kg/m3,

- thermal conductivity coefficient under operating conditions A, γ = 0.029 W/( m2. ° C ),

- in vapor impermeability coefficient - µ = 0.018 mg / (m of h Pa)

Then the calculated thickness of the insulation layer will be :

We accept the thickness of the insulation - an extruded polystyrene plate - 100 mm. We lay on the outer surface of the slab in two layers of 50 mm. (one of the standard slab index sizes) before placing a layer of cement brace.

The heat transfer resistance of the floor will be:

Thus, in further design calculations for the overlap we accept:

Reduced heat transfer resistance of the floor:

R0PR = R0USL. r = 3.81.0.75 = 2.87 m2 ° C/W.

Heat transfer coefficient of the floor :

RC. = 1/R0PR = 1/2.87 = 0.35 W / (sq.m. ° C).

3. Select to fill the window and door openings.

The design heat transfer resistance based on the energy saving conditions in the design cold period for windows was R0TP = 0.34 m2 ° C/W.

For installation in the building we accept, in agreement with the customer, the structure of the window (Appendix 6 * SNiP II379 *) with equal or nearest high heat transfer resistance .

This is a window with single-chamber glazing in aluminum bindings made of ordinary glass.

The reduced resistance of the selected window is R0PR = 0.34 m2 ° C/W.

Window K heat transfer coefficient = 1/R0PR = 1/0.34 = 2.94 W / (sq.m. ° C).

For external doors, the required heat transfer resistance shall be, in accordance with item 5.7 of SNiP 23022003 "Thermal protection of buildings" at least 0,6•RoTP external walls of buildings, where RoTP - resistance to heat transfer of walls, determined based on sanitary and hygienic conditions by the formula:

Glass doors with selective coating are single, installed at the entrance to the stairwell and exit to the balcony from the corridor with the following parameters :

The specified resistance to a heat transfer - R0PR = 0.65 sq.m ºС/Вт

Heat transfer coefficient To = 1/R0PR = 1/0.65 = 1.54 W / (sq.m. ° C)

Doors made of glass with selective coating are double (with tambour), installed at the entrance to the building and exit to the balcony from the hall with the following parameters :

The specified resistance to a heat transfer - R0PR = 0.72 sq.m ºС/Вт

Heat transfer coefficient To = 1/R0PR = 1/0.34 = 3.71 W / (sq.m. ° C)

4. Evaluation of humidity mode of external enclosures.

The condition of condensate precipitation is the formation of temperature on any surface or in the thickness of the fence below the dew point. Otherwise, the same condition can be formulated as obtaining in the calculation of the partial pressure of water vapors on any surface or in the thickness of the enclosure, which exceeds the pressure of saturated water vapors at the same temperature as it cannot be. This indicates that we are not dealing with steam, but with condensed water.

Since humidity processes take place slowly and do not have time to respond to short changes in ambient air temperature, the coldest month of the year is taken as the calculated, most dangerous period in terms of the possibility of condensate precipitation. The calculation is carried out according to the averages of this month. However, due to the fact that the monthly average temperature and partial pressure of water vapors are averaged separately, and the relative humidity in the cold period of the year is quite high, there are frequent cases when the monthly average partial pressure of water vapors is higher than the saturation pressure of water vapors at the monthly average ambient temperature. To eliminate a physically unacceptable situation, the partial pressure of water vapors is taken into account, which does not exceed the maximum possible partial pressure of water vapors at an average monthly temperature.

1. Check of condensation of water vapors on the inner surface of the outer wall.

In order to avoid condensation of water vapors on the inner surface of external enclosures (layers of enclosures), it is necessary that their temperature be higher than the dew point temperature tp by 1.5 - 2 ° С .

We determine the temperature of the inner surface of the outer wall tf by the formula:

We determine dew point temperature tp for room air with temperature tc = 20 ° С and relative humidity, in = 50%.

According to Appendix "L," SP 231012000 "Design of thermal protection of buildings" -

Partial pressure of water vapor of damp air in a condition of saturation (elasticity of saturated water vapor), according to the joint venture 231012000 "Design of thermal protection of buildings", Appendix M, table M.2., at tv = 20 °C will make

E = 2338 Pa = 23.38 hPa.

Then the elasticity of water vapor - e - at tv = 20 °C and φв = 50% will be:

Note:

The design humidity of the internal air shall be taken to be? = 50% (according to SNiP 23022003 "Thermal protection of buildings," Note to item 5.9 "Relative humidity of the internal air for determination of dew point temperature...... shall be taken to be:... for public buildings (except above) - 50%)

The received value of elasticity of water vapor of air will be sating at e = 1169 Pas at a temperature of 9.3 °C (the joint venture 231012000 "Design of thermal protection of buildings", Appendix M, table M.2.).

Also, the dew point temperature value is obtained graphically using the i-d wet air diagram (Fig.2.3.).

We receive as follows: We find a point with the tv parameters = 20 °C and φв = 50%.

We conduct the beam down (d = const) to the intersection with A = 100%.

The isotherm passing through the intersection point will correspond to dew point temperature tp = 9.3 ° С

We determine the temperature difference :

> 1,5 … 2 ° C, therefore, condensation of water vapors on the inner surface of the wall will not occur.

2. Check of condensation of water vapors on the wall surface at the place of thermal connection.

We will check the possibility of condensation of water vapors on the wall surface at the place of thermal connection .

The design of the wall with a thermally conductive connection (taking into account the above calculations) is shown in Fig. 2.4.

1st layer - external plaster, δ = 0.02 m., γ = 0.7 W/( m2. ° C),

The 2nd layer is a polystyrene insulation, δ = 0.06 m, γ = 0.029 W/( m2. ° C),

The 3rd layer is cellular concrete blocks, δ = 0.2 m, γ = 0.41 W/( m2. ° C),

The 4th layer is internal plaster, δ = 0.02 m, γ = 0.76 W/( m2. ° C),

The 5th - reinforced concrete, and = 0.2 m, with = 0.22 m, λ = 1.92 W / (sq.m. ° C ).

It is determined resistance to heat transfer Rt and temperature of inner surface of wall tf in section of heat-conducting connection by formula:

The actual temperature of the inner surface in the section of the thermally conductive connection is calculated by the formula:

At values: a/δ = 0.22/0.3 = 0.73 and c/δ = 0.22/0.3 = 0.73, αt/a = 1.92/0.74 = 2.6, switching scheme according to SNiP II379 *, Appendix 5 *, we find according to SP 231012004 "Design of thermal protection of buildings," Appendix I, Table I.1., the value of coefficient? = 1.02.

Since 18.2 ˃ 9.28 ° C, i.e., tx ˃ tp, there will be no condensation of water vapors on the inner surface of the wall at the place of thermal connection .

3. Check for no condensation of water vapors in the outer wall thickness.

Required fence design parameters for subsequent calculations:

Design temperature of internal air in tv = 20 °C,

The design humidity in the room is in = 50%.

Outside air parameters are accepted for the city of Chimkent, outside temperature, equal to the average temperature of the coldest month - January - txm = - 2 ° C, humidity ¼ n = 75%.

We determine the temperature distribution along the section of the wall, the scheme of symbols of which is shown in Figure 2.5.

The temperature is determined by the formula :

R0 = 2.72 m2 ° C/W - resistance to heat transfer of the outer wall,

RX-B - total heat transfer resistance of the layers (any point in the wall thickness) of the wall from the inner surface

We determine the partial pressure of water vapor of damp air in a condition of saturation corresponding to temperature in rated sections of an external wall (the joint venture 231012000 "Design of thermal protection of buildings", Appendix M (help), the Tab. of M.1 and M.2.):

We determine the elasticity of water vapors in the outdoor air and the indoor air of the room

relative air humidity, design humidity of internal air φВ = 50%, (according to Construction Norms and Regulations 23022003 "Thermal protection of buildings", the Note to item 5.9 or the joint venture 231012004 "Design of thermal protection of buildings), φН = 75% (Construction Norms and Regulations 230199 * "Construction climatology"),

- Е - the partial pressure of water vapor of damp air in a condition of saturation at the corresponding temperature in rated sections accepted on the joint venture 231012004 "Design of thermal protection of buildings", Prilozh. With (help), the Tab. of Page 1 and Page 2.

Then eB = eB. φВ = 2384. 0.5 = 1169 Pa

eH = EN. φВ = 517. 0.75 = 388 Pa

Since eH = 4.0 hPa = 400 Pa is the average for the coldest month of the year (January) partial pressure of water vapor as per SNiP 230199 * "Construction climatology," Table 5a "Average monthly and annual partial pressure of water vapor, hPa") more than the maximum possible value at the average temperature of -2 ° С in January, the calculated value of the partial pressure of outdoor water vapor is taken to be eH = 388 Pa.

We determine the total steam permeability resistance of the outer wall by the formula:

Steam permeability resistance on the inner and outer surface of the outer wall is accepted accordingly:

Rp.v = 0.026 (m2 • h • Pa )/mg

Rp.n = 0.013 (m2 • h • Pa )/mg

Then the total steam permeability resistance of the outer wall will be:

We determine the distribution of partial pressure of water vapors along the wall section.

The partial pressure of water vapour at any point x in the wall section is:

R.Px-c and R.Px-n - resistance to steam permeation of part of the outer wall from the point under consideration to internal or external air, (m2. h. Pa )/mg

Then the values ​ ​ of the elasticity of water vapors in characteristic sections along the thickness of the wall will be:

We summarize all the obtained calculation results into a table:

Plot changes of partial pressures in wall thickness (Fig.2.6)

The analysis of the temperature and partial pressure graph in the enclosure thickness shows the absence of a condensation zone (Ex > ex), therefore, an additional steam insulation device is essentially not required.

Calculation of the humidity mode of the fence according to the Wlag program and the results of the calculation:

Total steam permeability resistance of RPO fence = 5.61 m2.Pas/mg,

Steam permeability resistance from the inner medium to the plane of possible condensation RP.VN = 5.4 m2.has/mg .

This is more than required under the first condition of inadmissibility of moisture accumulation in the enclosing structure for the annual period (RP.VN = 5.4 > RP.1.TP = 0.11).

But it is enough to satisfy the second condition of moisture limitation in the enclosure for the period with negative average monthly ambient air temperatures (RP.VN = 5.4 > RP.2.TP = 0.76 ).

No increase in layer resistance from the inner medium to the plane of possible condensation is required

4. Check of enclosing structures for air permeability.

Air permeability of the outer wall.

Required fence design parameters for subsequent calculations:

Air permeability is determined by SP 231012004 "Design of thermal protection of buildings," Section 12, Table 17..

Calculations are made in accordance with Section 12 of the same SP 231012004 and Section 8 of SNiP 23022003 "Thermal protection of buildings."

We determine ∆R, Pa - difference of air pressures on both sides of the fence by the formula (SNiP 23022003 "Thermal protection of buildings," item 8.2.

We determine the pressure difference

Determine the required air permeability resistance:

Standard air permeability - GH - for external walls as per SNiP 23022003 "Thermal protection of buildings," Section 8., Table 11, is 0.5 kg/( m2 • h).

The actual air permeation resistance for this outer wall structure is:

372 ˃ 22.6 that is, Ru ˃ Rutr, thus the outer wall meets the requirements of SNiP according to the air permeation conditions.

Air permeability of windows.

To determine the required window density, find the required resistance to air permeation (SNiP 23022003 "Thermal protection of buildings," item 8.4.)

- GH - normalized air permeability of enclosing structures (SNiP 23022003 "Thermal protection of buildings," Table 11., for windows and balcony doors of residential, public and domestic buildings and premises in plastic or aluminum bindings is GH = 5 kg/pm2;

- ∆R0 - difference of air pressures on both sides of the window at which the

examination of air permeability of windows ∆R0 = 10 Pa,

Required air permeation resistance, thus:

- RITP = (1/5). (11.3/10) 2/3 = 0.27 m2.h/kg

The actual window permeation resistance must be equal to or greater than the required RIF ≥ RITP.

Therefore, the value of the air permeability resistance in this case is taken as RIF = 0.27 m2.h/kg. In the future, the Customer is provided with requirements for the purchase of windows, in which, according to the certificate, the air permeability resistance should be not less than the required RIF = 0.27 m2.h/kg.

5. Definition of heat losses through enclosing structures.

Heat losses through external fences are determined by summing heat losses through each external fence calculated by formula:

SNiP 23022003 "Thermal protection of buildings" or Table 3 * SNiP II379 * "Construction heat engineering";

- β-additive to the main heat losses, depending on the orientation of the fence and the angular position.

The addition to the orientation of the fence on the sides of the horizon is accepted for all external vertical and inclined (in projection to the vertical) fences facing:

- to the north, east, northeast and northwest in the size = 0.1;

- to the west and southeast = 0.05 from the main heat losses through these fences.

Schematically, the orientation additives are shown in the figure on the right.

Addition for blasting into buildings and structures of cold air through entrances not equipped with air and air-heat curtains is accepted at building height H, m, in size:

- for single doors - 0.22N;

- for double doors with tambour between them - 0.27N ;

- the same, but without vestibule - 0.34N;

- at presence of two tambours between triple doors - 0.2N

Rules for measuring the surface of a space enclosing structure.

Exterior Walls:

• Length of external walls of non-angular rooms is taken along external surface from external angles to axes of internal walls.

• Length of external walls of non-angular rooms is taken by distance between axes of internal walls.

The height of the external walls in sections of the building is on the first floor from the external surface of the floor located directly on the ground to the level of the clean floor of the second floor.

• On the middle floors - from the floor surface to the floor surface of the upper floor.

• On the top floor from the floor surface to the top of the floor structure.

Interior Walls:

To calculate the surface area of internal walls according to plans, the length of walls from the internal surface of external walls to the axes of internal walls or between the axes of internal walls is summarized. In size - the height of the walls from the floor surface to the ceiling surface.

Windows, doors, gates:

The area of ​ ​ windows, doors, gates is determined by the smallest sizes of building openings.

Slabs:

Area of ceilings is measured between axes of internal walls and internal surface of external walls.

Floors:

Area of zones with width of 2 m is determined.

Note

1. If in an adjacent cooler room the air temperature is lower by more than 3 then heat losses are calculated through the fence separating these rooms. Note here that air temperature is equal in cooler room.

2. In the calculation of heat loss, the Kokna value is taken with the Kstena deduction, since the wall areas are taken taking into account the window area.

Heat transfer coefficients of enclosures are accepted as per Table 2.8. below.

We calculate heat loss through enclosing structures according to the corresponding formula specified above. The required dimensions and areas are determined in accordance with the rules for measuring the enclosing structures of the room and using the functionality of the AutoCAD program on the drawings.

The calculation results are summarized in the table of Appendix No. 1. "Heat Loss Calculation Table"

6. Determination of heat flow rate for heating of infiltrating outdoor air.

Heat flow rate for air heating is determined by formula

Section 3

Heating.

3.1. Select and design a heating system.

Heat supply of the building is carried out from a boiler house separate on the territory of the design object.

The pressure in the heat supply line is 150 kPa.

Pressure in the return pipeline is 80kPa.

Coolant parameters in the building heating system from the boiler room 9570 ° С.

Three heating systems are designed in the building, which differ from each other in operating modes:

Heating system No. 1. Heating of auxiliary premises of the office part (bathrooms, dressing rooms, etc.), operating at night in standby heating mode;

Heating system No. 2. Heating of the base part of the building (technical rooms, ventilation chambers, electric panels, heat station, etc.), operating constantly in the same mode since all technical services are concentrated in the basement rooms, which involve round-the-clock duty ;

Heating system No. 3. Heating staircases. Staircases devices are located in the area of possible freezing of devices, so heating devices are connected according to a flow scheme without installing control and disconnecting valves.

For the main office premises of the 2nd and 3rd floors, a cooling system has been developed using fan coils (fan finishers), which work as air heaters in the cold period of the year and as air coolers in the warm period of the year.

For more stable hydraulic operation of heat and cold supply systems in different modes, a 4-pipe system is adopted - hot water circulates through the primary circuit pipes, and cold water circulates through the secondary circuit pipes in a warm period.

A more detailed description of cold supply is given in Section 5 of this Explanatory Note "Cold Supply."

The connection scheme to the heating network is independent for fancoyles, dependent on the heating and ventilation system .

Heating system No. 1 is adopted double-tube, vertical, with lower wiring, with dead end water movement. In this heating system, there are rooms with heating devices that are located on the same floor and the laying of vertical risers is impractical (for example, dressing rooms of the 1st and 2nd floors), and horizontal branches are adopted, which will be considered as separate risers of this heating system .

Thus, in this system there are three vertical risers and two horizontal branches.

Danfos control valves are installed on the instruments of this heating system. (see Figure 3.1). On the supply pipeline - RTDN type high hydraulic resistance valves, straight with preconfiguration. Adjustment indices are determined during hydraulic calculation of heating systems. Setup is performed during installation works. It can be locked by a special ring.

On the return pipeline - shut-off valves of RLV type, which are intended for use, in double-tube water heating pump systems in order to turn off a separate heating device for its dismantling or maintenance without emptying the entire system.

Heating system No. 2 (heating of the basement rooms) - double-tube, horizontal with associated coolant movement. On the devices of this system, Danfos control valves are also installed, as for system No. 1.

The appearance of the valves is shown in Figure 3.2. (a, b).

Technical descriptions of RTDN and RLV valves are given in Appendix No. 2 to the Explanatory Note "Heating System Control Valves."

Heating system No. 3, vertical with devices connected according to a flow scheme since there is a danger of water freezing in pipes and instruments on staircases .

Instruments of this system are connected according to flow diagram without regulating and disconnecting valves.

The main pipelines of these three systems are laid open under the ceiling of the basement in isolation to reduce heat loss in the main lines. The main pipelines are laid with a slope towards the drain during repair of the systems. Water discharge from the systems is assumed at the heat point to the drain pit, from which water is removed to the storm sewer.

The main pipelines of heating system No. 1 are laid 500 mm below the ceiling in order to provide a place for the shutoff valves of the risers.

Heating system pipelines - water and gas pipelines as per GOST 326275 *.

The heat supply system of fancoyles (wall fan finishers) is adopted horizontal, double-tube with associated movement for the coolant circuit.

The fan oil heat supply system is provided closed, through a plate heat exchanger, with forced circulation of the coolant.

Parameters of closed circuit coolant 8060 ° С.

Connection of funcoils to the main pipelines of the heat supply circuits is carried out both on the supply and on the return pipeline through the ball and coupling valve.

On the supply pipeline, after the ball valve, a three-way control valve is connected, which is supplied with a funcoil.

Air temperature is controlled from the built-in control panel of the fan finisher.

Floor pipelines of these systems are laid closed in the floor structure of the serviced floor with installation of panels in the floor for maintenance of control valves .

Thus, heat transfer of pipes for these systems is not taken into account .

The main pipelines of these systems are also under the ceiling of the basement with a slope towards the drain and are isolated by tubular insulation.

Pipelines of heat and cold supply systems - polypropylene in connection with aluminum. Main heat supply pipelines - electric welded as per GOST 1070491.

3.2. Hydraulic calculation

Hydraulic calculation of the system is performed by specific linear pressure losses (based on the accepted water flow rate in the pipes, when their diameter is selected).

The purpose of the hydraulic calculation is to determine the pipe diameters of all sections of the systems and the head necessary for the stable operation of the system.

For each heating system, a layout with arrangement of devices is drawn, the load on each device is determined and hydraulic calculation of heating systems is carried out with the connection of all branches .

Hydraulic calculation starts with heating system No. 1.

Pressure losses in the system are defined as the sum of linear pressure losses and local hydraulic resistances in the BCC according to the formula:

ΔРс = (RL+Z) OCK

The heating system is accepted as double-tube with dead end water movement.

Risers with double-sided connection of instruments, and two horizontally located risers.

The design of the heating system diagram for hydraulic calculation begins with the distribution of the heat load on the heating devices. All risers on the diagram are numbered according to the plans.

The main circulation ring (BCC) is selected by the most extended and loaded part of the system. In our case, the DCC passes through the riser 3, since the riser 2, although located further from the control unit, is less loaded .

Calculation of BCC is performed by computer (Excel program) and is given in tabular form in Appendix No. 3 to Explanatory Note "Hydraulic Calculation of Heating System Pipelines."

Table type, main columns and key figures:

Columns 1-4 show the values from the calculation heating scheme (see Working drawings).

Column 3 calculates the coolant flow rate in the section by the formula:

3.6 - translation coefficient, kJ/( Wh);

Q - heat load on the site, W;

β1 - coefficient of additional heat flow of installed heating devices at rounding in excess of the calculated value = 1.03 according to Table 9.4 "Internal sanitary and technical devices," Designer's Handbook, Part 1. Heating;

β2 - coefficient of accounting for additional heat losses by heating devices located near the external walls = 1.02 according to Table 9.5 "Internal Sanitary and Technical Devices," Designer's Handbook, Part 1. Heating;

s - specific heat capacity of water equal to 4.187 kJ/( kg • ° С);

tg, to - temperature of supply and return water, ° С.

Column 5 shows the diameter of the section. The diameter is selected so that the water velocity in the area does not exceed 1 m/s. If the water velocity in the area is higher than these values, the diameter of the area increases.

The preliminary selection of the diameter of the conditional passage of steel water and gas pipes (GOST 326275 *) in the sections is selected according to Table II.1 of Appendix II of the Designer's Handbook "Internal Sanitary Devices," Part 1, Heating, focusing on the value of the calculated water flow rate in the section. The actual specific pressure loss and water flow rate are determined by the accepted pipe diameter and actual water flow rate as per the table, and data are entered in columns 6 and 8.

In graph 7, the sum of local resistance coefficients for each section is placed, which include taps, tees, crosses, etc.

Values of local resistance coefficients (KMC) are given in Table II.12 - II.20 of Appendix II of the Designer's Handbook "Internal Sanitary Devices," Part 1, Heating.

Column 9 calculates the linear losses on the site obtained by multiplying graphs 4 and 8.

Column 10 sets out local losses for the areas, which are determined according to Table II.3 of Appendix II of the Designer's Handbook "Internal Sanitary and Technical Devices," Part 1, Heating, depending on the calculated speed of water movement and the sum of local resistance factors (CMS) of the area.

Then, by adding the indicators, graphs 9 and 10 obtain the total head losses in the section .

By adding up all calculated losses on the site, we will determine the total losses in the CCC and compare them with the available pressure. For heating system No. 1, the pressure loss in the CCC is 1.868 kPa.

The secondary design ring is calculated in the same way. Losses in it are significantly lower than losses in the CCC and amount to 1.382 kPa..

Non-binding is:

ΔОЦК =100 • (ΔРОЦК - (Rl+Z) of VCK) / ΔРОЦК =100 • (1,8681,1,382)/1.868=26.1%.

For double-tube systems, the allowable value is ± 25%.

The resulting value slightly exceeds the allowed value by 1%.

The design in this case accepts (the thermal load of the RCC in relation to the RCC is much lower) - so that the system is hydraulically stable, we install a balancing valve on the branch to the RCC with a diameter of 15 mm to link the rings..

A balancing manual valve of type MSVBD from Danfos is accepted for installation. The appearance of the balancing valve is shown in Figure 3.3.

Technical description of the MSVBD balancing valve is given in Appendix No. 4 to the Explanatory Note "Heating System Balancing Valve."

The diameter of the balancing valve is selected depending on the flow rate of the coolant and the controlled pressure drop according to the diagram presented in the catalog of balancing valves of Danfos company according to the following formula

G- design coolant flow rate, m3/h;

ΔP - head loss at valve, bar

Coolant flow rate in the regulated area is 0.044 m3/h. The controlled pressure drop is:

ΔP = 1.868 - 1.382 = 0.486 kPa or 0.00486 ba, which corresponds to the setting of 2.1 valve Ǿ15 (according to the Technical description).

Heating system No. 2 - double-tube, horizontal with associated coolant movement.

The design head for systems with the associated movement of the coolant is calculated by one pipe - by the supply from the distribution manifold to the middle device on the branch, and by the return pipe from the middle device to the collection manifold .

The remaining branches are then calculated and linked together.

All data are entered in the table of hydraulic calculation of heating system pipelines - Appendix No. 3 to the Explanatory Note "Hydraulic Calculation of Heating System."

Similar to the heating system No. 2, we calculate the heating system of funcoils, which are also connected by a double-tube, horizontal system with the associated movement of the coolant.

All data are entered in the table of hydraulic calculation of pipelines of the fancoil heat supply system - Appendix No. 5 to the Explanatory Note "Hydraulic Calculation of the fancoil heat supply system."

Balancing of branches of the fan oil heat supply system is carried out by Danfoss ABQM automatic combined balancing valves. The appearance is shown in Figure 3.4.

Advantages of AB-QM

• Stable temperature control throughout the flow range.

• Stabilizing the differential pressure across the control valve, which in turn reduces the load on the control valve stem and increases its service life.

• ABQM valves are smoothly adjusted for any given flow rate.

• The valve is capable of constantly maintaining a given coolant flow rate, which guarantees the necessary distribution of heat or coolant over all elements of the system without additional energy costs.

• The valve combines two functions: the possibility of balancing and regulation, which allows you to reduce capital costs by 2 times.

• Automatic flow control reduces system commissioning costs.

• If the system is not fully installed, it is possible, using these valves, to start it in parts, for example, floor by floor.

The diameter of the valve is selected by the diameter of the pipeline and the speed of the coolant in it is checked, which should not exceed the speed of silent operation of the valve.

Technical descriptions of the ABQM balancing valve are given in Appendix No. 6 to the Explanatory Note "Balancing Valve of the Fan Oil Heat Supply System."

3.3. Design and composition of heat station equipment.

Independent connection of the heating system to the heating network is determined by the heat supply organization of the city.

In this project, heat supply is carried out from a separate own boiler house and approval is not required. All systems are connected according to the open scheme since parameters in a heating system of 9570 wasps that is admissible on norms for heating of all rooms.

In the THS system metalplastic pipes for which the optimum temperature of the heat carrier of 8060 wasps are laid. Thus, the connection of the TCS system is carried out according to a closed scheme, with the preparation of the coolant of the necessary parameters in the heat exchanger .

The main equipment of the heat station includes:

• cold supply system low-temperature water distribution and collection header,

• water-water plate heat exchanger,

• pump group (circulation, make-up),

• heating and heat supply system distribution and collection manifold,

• expansion tank,

• mud makers.

Heat point plan, axonometric diagrams are presented in Sheet-3 Working Drawings. The schematic diagram of the heat station is shown in drawing Sheet-4. Diagrams show:

• all shut-off valves on all branches and equipment piping;

• water descent and air removal points;

• Heating system makeup unit with water from the heating network;

• instrumentation

• heat metering devices.

We select the equipment of the heat station

After the introduction of the heating system into the building, disconnecting flange valves are installed from the outside diameter, the diameter of which is accepted according to the diameter of the Dy76 pipeline. On the supply and return pipeline, mud meters are installed in front of the heat meter along the water flow to protect the heat meter equipment from foreign inclusions.

We accept for installation of mud machines according to the data of ORGRES for Dy76 as per Table 33.13, Chapter 33, Builder's Handbook, "Installation of internal sanitary devices," with appropriate dimensions.

Distribution and collection header No. 2 are located on the supply and return pipelines, respectively, the diameter of which is selected based on the calculation: the cross-sectional area of ​ ​ the collector is equal to or more than the sum of the areas of all incoming pipelines. Thus, the diameter of the collector is assumed to be D 108x4 mm, 3 m long.

The manifolds consist of 5 branches:

• To heating system No. 1;

• To heating system No. 2;

• To heating system No. 3;

• To air heaters of ventilation and air conditioning systems;

• To water heaters of closed heating system of funkoil

Selection of heat exchanger.

Currently, the most widely used are detachable plate heat exchangers, in which the plates are separated from each other by rubber seals. Some of the main advantages are:

- Units and parts in such heat exchangers are completely unified;

- The main working parts are made by stamping and welding, which creates the possibility of economical mass production of such devices at minimum metal consumption;

- Installation and dismantling of these devices is carried out quite quickly;

- Cleaning surfaces requires little labor, ease of service;

- Plate heat exchangers have significantly smaller overall dimensions and metal consumption at equal heat load than other devices with sufficiently high heat exchange efficiency;

- High repairability of these devices.

The principle of operation of the plate water heater is shown in the figure below.

As a water heater, the project adopted a modern plate water heater from Danfos, which requires insignificant space and is installed on the floor.

The heater was selected using a program developed by Danfos and recommended for calculation.

The Danfoss Heat Exchanger Calculation Tool is designed to select plate heat exchangers from the standard standard series manufactured by Danfoss. You can view and print the calculation results directly from the calculation program window, or transfer the calculation data to a Microsoft Excel file.

Parameters of water of a contour of high temperature T11, T12 - 9570 °C, parameters of water of a contour of low temperature T21, T22 - 8060 °C.

Heat consumption according to calculation 39.5 kW.

Water flow rate - 0.76 l/s..

Note: Heat consumption is calculated from heat losses, minus rooms equipped with heating system.

For installation, the program issued several versions of detachable plate heat exchangers .

The most economical option with a surface reserve of 42.6% in the amount of 2 pieces (1 working, 1-standby) was accepted for installation. Heat exchanger type XG 18H130 number of plates 30 pieces.

XG 18 heat exchangers are designed for use in small heating and hot water supply systems, and perform the following main tasks:

- optimal thermal and hydraulic solution

- these heat exchangers are compact, light and inexpensive (which is important for use in block thermal points)

- have easily replaceable seals

The calculation form and technical description are attached in Appendix No. 4 to the Explanatory Note "Calculation Form and Technical Description of Heat Exchanger."

Connection of mains water is made from above and comes out from below, heated water is supplied from below and comes out from above, thus countercurrent flow between heating and heated water is provided.

Selection of pumps.

The design, in accordance with the assignment, coolant circulation for heating systems is carried out using pumps installed in the boiler room, and are not considered in this design.

Thus, we select circulation pumps for the fancoyl heat supply system.

Design pump pressure ΔRN, Pa, at independent scheme of connection to thermal network is determined by method, at which parameters of pipes diameters of heating system are accepted by permissible rate of coolant, and mark of circulation pump is selected at determination of actual pressure losses in system. Design pressure of the pump, we determine:

ΔPC = 13 kPa, head loss in the heating system;

ΔRTP = 70 kPa - head loss in the heating network pipelines;

ΔРТО = 16 kPa - losses of a pressure in heat exchangers and fittings in a binding,

ΔPE - natural circulation pressure, in this case is not taken into account, according to item 10.7 of the Designer's Handbook, Internal Sanitary and Technical Devices, Part 1, Heating .

Thus, the pumps are selected by the water flow rate in the heating system and by the required water head:

We select the pumps.

Pumps are selected by the water flow rate in the system and by the required head.

We accept the pumps of the leading imported manufacturer of Wilo pumps - the WiloTOPS 50/4 model pump, in the amount of 2 pieces (one main, the second standby). The pumps are selected according to the catalogue offered by Wilo available on the Internet.

Circulation pumps WiloTOPS with wet rotor, threaded or flanged connection. Used in heating and cooling systems, air conditioning from 20 ° C to + 130 ° C. Cataphoretic-coated pump housing (KTL) for corrosion protection during condensate formation. It has manual power adjustment with 3 stages of rotation speed. The maximum operating pressure at the standard design is 6 bar. Operation modes - "main/standby" (automatic switching of pumps by fault signal/by timer). The pump is equipped with heat insulation.

Pump Housing: Grey Cast Iron

Impeller: Synthetic material

Shaft: Stainless Steel

Bearings: Metallograph

Pumps are installed on the return pipeline of the fan oil heat supply system, to the heat exchangers. Check valves are installed on the pump pressure branch pipe.

The pumps are switched from main to standby automatically when the main one is stopped from the control board.

Make-up of the secondary circuit of the fan oil heat supply system is performed at actuation of the pressostat (electrical contact differential pressure switch).

The appearance of the pressostat is shown in the figure on the right .

The principle of operation is to open and close the electrical circuit depending on the change in pressure in the pipeline compared to the given one.

When the pressure in the return pipeline of the fancoyle heat supply system decreases, the pressostat gives an impulse to turn on the solenoid valve installed on the make-up pipeline.

Make-up pipeline and expansion pipe are connected to suction branch pipe of pumps.

Calculation of the expansion tank.

Expansion tanks (open and closed with an air or gas cushion) are used at a thermal power of the heating system of one or more buildings of not more than 6 MW (to which the designed object belongs).

Common previously open expansion tanks have a number of disadvantages, such as:

- increased evaporability of the liquid and the need for its constant replenishment;

- increased corrosion in the system due to oxygen access to it;

- more expensive installation of an open tank, since it should be installed in the uppermost part of the heating system, it is necessary to provide a special place and ensure its insulation and elimination of freezing. A closed tank can be installed anywhere;

- The open heating system operates at low pressure and is therefore difficult to control.

And at present, open tanks are practically not used.

Thus, the project adopted the installation of a modern closed membrane expansion tank.

The membrane expansion tank is a sealed vessel divided by the membrane into two parts. In one part there is always a constant amount of nitrogen (air), the other is filled with water as necessary.

The ELBI membrane expansion tank is designed to absorb the increasing volume of coolant in small heating systems and allows adjusting the operation of the heating plant. The closed ELBI expansion tanks consist of a steel body and a synthetic membrane that separates the heated coolant from the air-filled chamber.

The expansion tank is calculated according to the form proposed by the manufacturer ELBI (Italy), the procedure of which is given below.

To determine the working volume of the membrane expansion tank, it is necessary to determine the total volume of the heating system - C - by adding water volumes of heat exchangers, heating devices and pipelines. The capacity of the heating system is calculated in detail in accordance with § 10.6.8. Internal sanitary facilities, C.1. Heating, ed. I. G. Taroverov. M.: Stroyizdat, 1990, (Volume of water in elements of the heating system, Table 10.3.).

During calculations at the stage of feasibility study, preliminary calculations of engineering design solutions, it is allowed to take the specific capacity of the system - 15 l/kW.

We make a preliminary calculation.

The capacity of the heating system of fancoyles is 39.5 kW ,

Then the capacity of the system will be:

C = 15 x 39.5 = 592.5 l.

The volume of the expansion tank is determined by the formula:

Vb = C • β/( 1-Pmin/Pmax),

- β-liquid expansion coefficient (Table 10.2. "Volumetric expansion of water heated in the heating system," Internal sanitary devices, Ch.1. Heating, ed. I. G. Taroverov. M.: Stroyizdat, 1990).

We accept the coefficient both when filling with tap water (10 ° C) and the maximum inlet temperature (90 ° C), β = 0.022 ,

Pmax - maximum operating pressure of the system (design pressure of the safety valve), 2.5 bar is usually enough for public buildings;

Pmin - air pressure in the membrane expansion tank (must be not less than the hydrostatic pressure of the heating system at the tank installation point), we take 150 kPa (1.5 bar).

By substituting all values in the tank calculation formula we get the value of 34 l.

The calculation form is given in Appendix No. 8 of this Explanatory Note "Calculation of the expansion tank."

Thus, the ERCE 35 tank is accepted for installation by the project.

Height - 390 mm, diameter 400 mm..

Maximum operating pressure - 10 bar

Gas cushion pressure - 1.5 bar

Operating temperature range from 10 ° С to + 100 ° С.

Device and operating principle:

The tank housing is made of carbon steel.

Inside the housing 1 of 8500l tanks there is a non-replaceable membrane 2 made of styrene-butadiene rubber (SBR), embedded in the folded joint of the housing parts, dividing the housing into liquid (top) and gas (cavity) cavities (see Figure). Top of tank has connecting union 3 with external thread. At the bottom of the housing there is a nipple 4 connected to the gas cavity. The nipple allows maintaining the design air cushion pressure. Tanks with a volume of 35l or more have mounting legs 5 (there are tanks 35 and 50l without legs).

External surface of tanks is covered with thermostabilized red epoxy enamel (RAL 3000). Tanks with a volume of 750 and more liters have a replaceable membrane.

3.4. Thermal Calculation of Heating Appliances

The design provides for the following heating devices:

- MS90108 radiators and smooth pipe registers are installed in technical and process rooms.

- in the auxiliary rooms of the office, bathrooms and staircases, radiators of the improved design of the Calidor Super Alternum series are installed.

Heating devices shall be placed open, at the outer walls and under the windows at a distance of not less than 60 mm from the clean floor and 25 mm from the wall in places accessible for inspection, repair and cleaning. On staircases, heating devices are installed only in the lower part .

To exhaust air from the system, a Mayevsky valve or automatic air sink is installed in the upper plugs of the upper floor instruments with the lower location of the supply and return lines.

On the staircases there are separate risers with the connection of heating devices according to a flowing unregulated scheme.

Characteristics of heating appliances.

1. Technical characteristics of cast iron section radiator MS90108 as per Appendix X, Table X.1, "Technical characteristics of heating appliances," Internal sanitary devices, Part 1. Heating:

- heating surface area - A = 0.2 m2,.

- rated heat flow of one section - Qp = 140 W

2. Registers made of smooth pipes with horizontal channels in a single-row design, two pipes with a diameter of 50 mm, a length of 1.5 m each.

- heating surface area - A = 0.94 m2,.

- nominal heat flow - Qp = 123 W

3. Calidor Super Alternative radiators according to the manufacturer:

- heating surface area - no data,

- rated heat flow of one section - Qp = 144 W

The number of elements N in the sectional device is determined by the formula

QPR - required design heat transfer of the device;

QT.P - heat flow of instrument unit;

β3 - correction factor taking into account the number of sections in the device and determined in accordance with the recommendations in item 9.5 "Internal sanitary and technical devices," Designer's Handbook, part 1. Heating, up to 15 sections is taken equal to 1.

β4 - correction factor, which takes into account the method of installation of the device in the room and is determined according to Table 9.12, ibid., for an open installation it is taken equal to 1.

The rounding of the fractional number N to the integer is carried out, upwards .

The required heat removal of the device is calculated taking into account the heat removal of pipes (risers, branches, pipelines) open in the heated room: QPR = QP - 0.9 • QTP

Pipelines within the premises are laid openly, so their heat removal is taken into account and determined by the formula:

Qtp = qlv + qglg,

Where:

qv, qg is a teplootacha of 1 m of vertical and horizontal pipes, W/m, is determined by the tab. II.22 and II.24 "Internal sanitary devices, the Reference book by the designer. Part 1, Heating ";

lv, lg is length of the pipes laid horizontally and vertically indoors.

Heat flow from the radiator section or unit of another heating device is determined by the formula:

QP - nominal conditional heat flow of the device, W.

GPR - design water flow rate in the instrument, according to the design table of hydraulic calculation of the heating system and is 15.8 kg/h;

n, p, c - experimental numerical indicators according to Table 9.2 (page 44, "Internal sanitary and technical devices," Ch.1. Heating);

b - coefficient of atmospheric pressure in the construction area as per Table 9.1 "Internal sanitary and technical devices," Ch.1. Heating. For the calculated barometric pressure of 1010 hPa (see Initial data), the coefficient is 1.

ψ - coefficient of accounting of the direction of the movement of water in the device. We take it equal to 1.

Δtcp - average temperature head in the device is:

For heating system No. 2, we will select the number of sections to the Service Room device in the axes AB/910 .

The heat loss of the room is 620 watts. Considering heat transfer of pipes:

QP = 140 W.

When connecting the device according to the "downgrading" scheme for cast iron radiators n = 0.15; The actual heat dissipation of the heating device will be:

We determine the number of radiator sections for our device:

Hereinafter, the rounding of the fractional number N to the integer is carried out, upwards. Reduction of design area of device Ar is permissible by not more than 5%.

The nearest larger integer number of sections is accepted. At N = 5

We calculate all heating appliances.

Section 4

Ventilation and air conditioning

4. Ventilation and air conditioning

Mechanical plenum ventilation systems are designed in the ventilation and air conditioning design of this project.

In all main rooms the central conditioning (premises of offices, service premises, operator halls, etc.), the forced and exhaust ventilation is provided.

In the Server Data Center room in the basement air cooling with self-contained precision air conditioners. A description of the precision air conditioning system is given in section 6 of this Explanatory Note.

At the customer's request, in office and office rooms on the first and second floors, a system of fancoyles is provided, operating in two modes as internal air heaters in winter and air coolers in summer.

The fancoyles of the operating rooms of the 2nd floor work for recirculation, that is, by taking air from the serviced room, they heat it in plate heat exchangers in the winter and cool it in the summer.

In the remaining rooms, the supply of heated in the cold period and purified air is provided. In a warm period, the supply air is cleaned only of dust.

Air exchange of premises is determined by sanitary standards and standards of multiplicity of supply air supply, but not less than indicators of sanitary standards.

Sanitary norm is the minimum amount of outdoor air that must be supplied to one person in the serviced room. For calculations, the largest of the two obtained values is taken.

As a rule, this value is the sanitary norm of outdoor air.

The sanitary norm is determined according to table M.1 of SNiP 41012003 "Heating, ventilation and air conditioning," and is - 40m3/hour for office and office premises, and 20 m3/hour for public service premises .

Heat supply of plenum plants is carried out by heat carrier - water with parameters 95 ° С - 70 ° С.

In the plant serving office and office premises, a heat disposal system is provided.

Since the sanitary norm of outdoor air is adopted in the calculation of air exchange, recirculation is impossible.

In this regard, the heat of the exhaust air is disposed of using a recuperator. In this design, a rotary plant is adopted as a recuperator, in which heat is exchanged between the outgoing air and external cold air in winter without mixing them.

Building rooms located on the 1st and 2nd floors have corridors in which there are external fences with windows, so smoke removal from these corridors is not required. In the basement there is a corridor more than 15 meters long without natural light, so smoke removal is organized in case of a fire in the corridor. Smoke removal is carried out through a valve located under the basement ceiling and triggered by fire detectors located in the basement corridor. When the smoke removal valve is activated, the smoke removal fan is automatically activated. A roof smoke removal fan of the Veza plant was accepted for installation. Fans of this class are designed to remove smoke with a temperature of 350400 ° C.

To prevent smoke penetration through ventilation systems to other floors, universal fire-retardant valves of VEZA KPU1M are installed on the ducts of general ventilation systems.

For more detailed solutions on smoke protection refer to item 4.3. this Explanatory Note.

Carrier equipment was used as equipment for central air conditioning systems and exhaust systems.

Air distribution devices - BETA - air distribution diffusers with adjustable air flow. Air distribution is carried out with four-sided staining jets.

On air ducts of plenum and exhaust systems, normally open valves are used, which are open under normal operating conditions. In the event of a fire, they automatically close and prevent combustion products from entering adjacent floors through air ducts.

In smoke removal systems, the same smoke valves with the function "normally closed" are used, i.e. in normal operation they are closed, but when a fire occurs, they open, the smoke removal fan is turned on and the combustion products are removed.

Throttle valves are installed on air ducts branches during adjustment and operation of general ventilation systems.

4.1. Determination of heat, moisture and harmful emissions.

4.1.1. Calculation of heat inputs.

Heat input in rooms is determined by the formula:

Q = Q1 + Q2 + Q3 + Q4 + Q5, W,

Where:

Q1 - heat emissions from solar radiation.

Q2 - heat input from electric lighting

Q3 - heat input from heating.

Q4 - heat inputs from indoor people.

Q5 - heat input from equipment installed in the premises.

Heat inputs to the room from heating devices are supposed to not be taken into account due to the equipment of the system with automatic temperature controllers on the supplies to the devices.

It is also accepted that the main heat emissions in the warm period of the year in the main office premises of the building are disposed of by fancoyles.

The calculation will be carried out for the air conditioning system of the room of Operation Room No. 1 in the summer.

Similar calculations are made for the remaining premises. All calculation data are entered in the table Appendix No. 10 "Heat Input to Premises "

The total area of ​ ​ operating room No. 1 is 317 m2.

The number of employees in the hall in accordance with the technological assignment is 5 people, and the number of visitors is 30 people.

When calculating emissions of heat, moisture and harmful substances, reference data and methodology are used:

Chapter 2, Designer's Guide. Internal sanitary facilities, Part 3, Annex 1,

Chapter 6, Educational edition. Ventilation., P. N. Kamenev, E. I. Tertichnik .

and other reference and regulatory sources.

Maintenance staff - 3 women; 2 - men. Visitors:

women - 15 people

men - 15 people.

Heat emissions from people

Warm period: tv = 25 °C

The amount of explicit heat from people:

Qch.y.l = 65 W/person

Qch.y.sec = 70 W/person

Qch.y. = 65 • 0.85 • 15 + 15 • • 65 + 70 • 0.85 • 3 + 70 • 2 = 2116 W

Total heat from people:

Qch.p.l = 146 w/person

Q.p.p. = 201 w/person

Qp.p. = 146 • 0.85 • 15 + 15 • • 146 + 201 • 0.85 • 3 + 201 • 2 = 4966 W

Cold period: tv = 20 °C

Qch.y.l = 93 W/person

Qch.y.sec = 98 W/person

Qch.y. = 93 • 0.85 • 15 + 15 • 93 + 98 • • 0.85 • 3 + 98 • 2 = 3027 w

Qch.p.l = 149 W/person

Q.p.p. = 204 W/person

Qp.p. = 149 • 0.85 • 15 + 15 • • 149 + 204 • 0.85 • 3 + 204 • 2 = 5063 W

Heat inputs from artificial lighting

QOCB = E • FPL • qosv • ¼ osv, W

where:

E is the general lighting level of the premises, 200 lx in this case,

FPL - room floor area, 317 m2,

qosv - specific heat generation, W/m2, which is from 0.05 to 0.13 for fluorescent lamps. According to the project, the lamps are luminescent, 0.05 is accepted.

, the extent of the light energy entering the room is equal to 1 if the lamps are directly in the room.

Thus:

QoQ = 200 • 3178 • 0.05 = 31708 w

Heat emissions from solar radiation

Heat, Q W, in the room from solar radiation through glazed light openings and massive enclosing structures of buildings of various purposes for the hottest month of the year (July) and a given hour of day, should be calculated by the formula:

Q = ΑQi + ΟQim, W where,

QOCi - heat flow, W, through the i-th light opening

Qradi - heat flow, W, through the i-th massive fence

The amount of heat coming from solar radiation through massive fences (in this case, we determine the coating as the main one) is found in accordance with the procedure - Section 2.3. "Calculation of receipts of warmth to rooms", paragraph "Z", Reference book by the designer, Internal sanitary devices: Ventilation and air conditioning, Part 3,

The average daily heat input due to solar radiation through the coating is determined by the formula:

Qrad = k∙ (tnusl - tv) ∙F, W

where:

k - coating heat transfer coefficient, k = 0.35 W/m ² ° C (see section Construction heat engineering)

F = 1232 m ², surface area (roof) of calculated premises ,

Normal average daily outside air temperature

tnusl = tnA + soundJcp/αn = 33,6+0,9∙ 331/15 = 53.5 ° C

ρ - coefficient, absorption of a heat flux of an external surface of a covering = 0.9 (II379 Construction Norms and Regulations appendix 7 *),

Jcp - average daily amount of heat from total solar radiation Jcp = 331 W/m ² for latitude 44 ° (Table 2.12 of the Designer's Handbook)

αn - coefficient, heat transfer on the outer surface of the coating during the warm period of the year, αn =5+10∙√ν =5+10∙√1 = 15 W/m ² ° C

Qrad = 0,35∙ (53.5-25) ∙1231= 12 282W.

We accept 12,282 watts for further calculations.

The amount of heat supplied from solar radiation through the filling of light openings is determined in accordance with the procedure - Section 2.3. "Calculation of heat receipts to the premises," paragraph "G," Designer's Handbook, Internal Sanitary Devices: Ventilation and Air Conditioning, Part 3, Book 1..

The amount of heat supplied through the filling of light openings is calculated as a one-time heat supply through glazing on the sides of the world, and the largest one-time heat supplies through glazing are determined. These heat inputs are taken into account.

The heat flux, W, of solar radiation through the light opening is calculated by the formula:

Qoc i = (qp + qp) K1 • K2 • Aos,

Where:

qp, qp is the surface density of heat flow, W/sq.m., through a glazed light opening in July at a given hour of the day, from direct and scattered solar radiation, taken for vertical and horizontal glazing according to Table 2.3 of the Designer's Handbook. There are no sloping glazing in the building, so the entire calculation is done for vertical glazing surfaces.

The surface density of heat flow from direct and scattered radiation, depending on the graphical latitude of the building location point, is also given in the reference data of Manual 2.91 to SNiP 2.04.0591 "Calculation of the arrival of solar radiation heat into the premises." The geographical latitude of our building 44o.

K1 - heat transmission coefficient of sunscreens (curtains,

cornices, blinds and other products of factory manufacture), accepted as per Annex 8 of SNiP II379. In our case, curtains are made of light fabric, for which the coefficient is 0.4.

K2 - coefficient of heat transmission by glazing of light openings. In this case, double-layer double-glazed windows in metal bindings are adopted (coefficient is 0.68)

Aoc - area of ​ ​ a light opening (glazing), m ².

We give the data from the table for Operations Room No. 1:

For all rooms, the calculation is performed for three time-of-day periods:

From 9 to 10 hours

From 12 to 13 hours

From 16 to 17 hours

In the operating room No. 1 there are light openings in two orientations - U-B and S-Z. In the southeast direction there are 7 windows with dimensions of 1.6x1.8, in the northwest direction - 6 windows with the same dimensions. Heat penetrations for fences oriented to the southeast are :

From 9 to 10 hours - 387 W/m2

From 12 to 13 hours - 214 W/m2

From 16 to 17 hours - 55 W/m2

Heat inputs for fences oriented to the northwest are:

From 9 to 10 hours - 109 W/m2

From 12 to 13 hours 79 W/m2

From 16 to 17 hours 357 W/m2

Thus, the heat appearances through the light barriers oriented to the southeast will be:

From 9 to 10 hours - Q os = 387 W/m2 • 7 • 1.6 • 1, 8m2 = 7802 W

From 12 to 13 hours - Q os = 214 W/m2 * 7 • 1.6 • 1, 8m2 = 4314 W

From 16 to 17 hours - Q os = 55 W/m2 • 7 • 1.6 • 1, 8m2 = 1109 W

for fences oriented to the northwest are:

From 9 to 10 hours - Q os = 109 W/m2 • 6 • 1.6 • 1, 8m2 = 1884 W

From 12 to 13 hours - Q os = 79 W/m2 • 6 • 1.6 • 1, 8m2 = 1365 W

From 16 to 17 hours - Q os = 357 W/m2 • 6 • 1.6 • 1, 8m2 = 6169 W

Thus, heat inputs into the room of heat from solar radiation through light openings will be:

From 9 to 10 hours - Q os = 7802 + 1884 = 9685 W

From 12 to 13 hours - Q os = 4314 + 1365 = 5679 W

From 16 to 17 hours - Q os = 6169 + 1109 = 7278 W.

Heat inputs from equipment installed in the premises.

Computers are installed in offices and working rooms, during the operation of which heat is released to the premises. Depending on the type of computer, heat emissions vary.

We accept an average heat output of 300 W from the computer. The number of computers in the room is taken equal to the number of people in this room.

The number of people in each room is accepted according to the task of technologists, and in its absence - according to the norm of the area of ​ ​ the room per person. In our case, for office buildings, this norm is - 6 m2/person.

For the remaining rooms, the calculation of heat inputs is carried out in the same way as this.

4.1.2. Definition of Room Moisture Releases:

The sources of moisture entry into the room are people, technological equipment, hot food, etc. In some rooms (souls, laundry rooms, etc.), moisture release occurs from wetted surfaces of enclosing structures and equipment.

Moisture emissions from people are determined from the table "Amount of heat and moisture released by adults (men)" from Table 2.2. Designer's Handbook, Internal Sanitary Devices, Part 3, Part 1, Chapter 2, Paragraph "D."

Warm period:

for Operation Room No. 1 at internal air temperature 25 OS:

MPH = (115 • 15 + 115 • 0.85 • 15 + 3 • 185 + 2 • 0.85 • 185 )/1000 = 4.06 kg/h

Cold period:

at internal air temperature 18 OS

MPH = (71 • 15 + 71 • 15 • 0.85 + 3 • 131 + 2 • 131 • 0.85) = 2.59 kg/h

4.1.3. Determination of gas (harmful) emissions

The release into the room of carbon dioxide exhaled by people is determined in the same size for all periods of the year, taking into account the intensity of physical activity. Accepted:

mco2l = 25 l/hour x person

mco2cp = 35 l/h x person

Mco2 = 15 • 25 + 15 • • 0.85 • 25 + 3 • 35 + 0.85 • • 2 • 35 = 858 l/hour

Having calculated the moisture and gas emissions for Operation Room No. 1, all calculations are summarized in the table:

The same calculations are made for all rooms.

Having such data across all rooms, you can calculate the process beam in each room, if necessary.

4.2. Selection, description and calculation of fancoyles.

For the main office premises of the 2nd and 3rd floors, a cooling system has been developed using fan coils (fan finishers), which work as air heaters in the cold period of the year and as air coolers in the warm period of the year.

For more stable hydraulic operation of the system in different modes, a 4-pipe system is adopted - hot water circulates through the primary circuit pipes, and cold water circulates through the secondary circuit pipes in a warm period.

The project identified for installation Idrofan fan finishers, manufactured by Carrier, model range (series) 42N.

The appearance is shown in Figure 4.1.

This new lineup has concentrated the latest technologies, which is unusual enough for such non-complex equipment as fancoyle. As a result, it is easy for me to select the desired model and install it indoors.

These versions are available in any version: from models in the case for the floor or under the ceiling installation, to

models without housing, for hidden, false-ceiling horizontal or vertical mounting.

Benefits and Features:

- Due to the elegant shape of the polished housing, 42N fan finishers are perfectly combined with almost any interior of the room.

Pre-painted steel panels are protected against corrosion by finishing paint coating.

- Successful design of a cast plastic condensate collection tray allows the same unit to be installed both vertically and horizontally

no special accessories are required.

- For four-tube systems, the manufacturer shall install a cooling and heating heat exchanger during assembly.

- 42N fan shedders produce such low noise during operation that its level is accepted as a new standard of comfortable conditions for buildings.

- Electric motors. Idrofan Fan Finishers Come with Multiple

high-speed engines. The number of speeds has been increased to five to increase their usability for almost any application.

- Filters. The standard filter for Idrofan series blowers with a corrugated filter surface, which is 87% larger than the known conventional filters, has additional advantages: less air consumption per unit surface area (which provides less pressure drop and reduced noise level), the average interval between cleaning the filter is three times larger compared to conventional filters.

High-quality EU1 grade polypropylene is used in the manufacture of the filter. The filter is located in the lower part of the unit. To clean it, it is enough to remove the safety screw and manually disconnect the side elements of the filter. You can then extrude the filter frame and easily extract the filter itself. Assembly of the filter is done in reverse sequence and is also easy. The filter is clearly fixed in the place provided for it to prevent the passage of air past the filter and ensure high-quality filtration of the air supplied to the room.

- Easy and easy installation.

- The electronic thermostat has an elegant shape with two coaxial handles, with the help of which the user can set the temperature in the room and the speed of rotation of the fan.

More detailed technical parameters and characteristics are given in Appendix No. 11 to this Explanatory Note "Technical Description of Idrofan 42N Series Funkoil."

When calculating the type of funcoils and their quantity for installation in rooms, the following are taken into account:

- manufacturer's data on their cooling capacity and heating capacity, given in Table 4.2. "Physical and Electrical Characteristics of Funkoil, 4 Pipe System"

- design heat loss of the room as per Appendix No. 1 Explanatory notes,

- design heat inputs to the premises as per Appendix No. 10 of the Explanatory Note.

Installation locations are defined - under the window openings of the room. The design decision determined that compensation for heat losses in the room is provided by funcoils.

So, the heat input into the room of Operation Room No. 1 at different design times of the day is from 15.8 kW to 18.2 kW.

The number of window openings is 13.

We choose by the parameters of cooling capacity and fan operation at minimum speeds with minimum power consumption (in order to save power consumption) the type of fancoyles providing compensation for design heat inputs with a power reserve.

For installation in the Operating Room No. 1, the type of fancoyle is 42N20 in the amount of 13 pieces.

Cooling capacity - from 1.19 to 2.06 kW, at low fan speeds - from 1.19 to 1.451 kW.

Multiplying by 13 we get the total cooling capacity of fancoyles in the room equal to 15.5 kW to 18.8 kW (maximum - 26.7 kW).

The heat loss of the premises of Operation Room No. 1 is 10.6 kW.

The heating capacity of a 42N20 type fancoyle is from 1.83 kW, then the total heating capacity of fancoyles in the room will be 23.8 kW, which provides compensation for heating in the room, even with a significant margin.

In the same way, we select the type and number of fancoyles for all rooms.

Data are entered in the table of Appendix No. 10 of the Explanatory Note.

4.3. Determination of supply and exhaust air.

You can determine the supply air flow rate in several ways. For civilian buildings, the supply air flow rate in the air conditioning system is usually determined for the warm year period by excess apparent heat and is considered unchanged throughout the year.

By excess of apparent heat, the flow rate is considered by the formula:

depending on the air exchange method selected and the type of air distributor

Air exchange by moisture emissions, by released gas (harmful) emissions should be taken into account for the corresponding technological (production) premises. For public administrative civil buildings, it is much less than air exchange, determined by the multiplicity of air in the room, either by the sanitary norm of air supply per person, or by excess heat.

Thus, in this project, taking into account the fact that the bulk of heat is removed by fancoyles, the basis is the calculation of air according to the multiplicity or sanitary norm of air supply per person.

Calculation by normalized air exchange multiplicity is used for rooms for which air exchange multiplicities can be determined by SNiP by inflow and by exhaust:

For individual rooms, air exchange can be calculated based on the rated specific flow rate of supply or removed air:

Calculation of supply air, according to the sanitary norm of fresh air supply per person:

The total area of ​ ​ operating room No. 1 is 317 m2 .

The number of employees in this hall according to the technological assignment is 5 people, and the number of visitors is 30 people.

According to Table 1M SNiPa 410103, the minimum amount of outdoor air for public premises with natural ventilation per permanent person (type of work - medium severity) is 40m3/hour per person.

Thus, the amount of air supplied by the employee in this room will be:

the number of visitors will be 25 people (the type of work is light ).

The rate of outdoor air consumption per person with a temporary stay (less than 2 hours) will be 20 m3/hour per person.

The amount of air supplied to visitors will be:

L = 20 • 25 = 500 m3/h,

The total amount of fresh air of this room will be 700 m3

The total area of ​ ​ operating room No. 2 is 386 m2/h.

Maintenance staff - 3 women; 2 - men.

Visitors: 30 people.

The amount of air supplied to employees in this room will be:

L = 40 • 5 = 200m3/hour,

the number of visitors will be 25 people (the type of work is light). The rate of outdoor air consumption per person with a temporary stay (less than 2 hours) will be 20 m3/hour per person. The amount of air supplied to visitors will be:

L = 20 • 30 = 600 m3/h,

The total amount of supply air for these two operating rooms will be 1500 m3/h.

The project provides a separate plenum system (P2) for servicing the operating rooms. The installation will be selected accordingly for a given amount of air.

Supply air calculation adopted by the project:

The maximum air exchange determined by the sanitary norm of fresh air supply per person or by the multiplicity of air exchange is taken as the calculated air exchange in the premises.

All data of room air exchange calculations are entered in the table Appendix No. 12 "Air exchange calculation"

4.4. Selection of ventilation and air conditioning system diagram.

Two plenum and six exhaust systems were designed in the building. P1 system is designed for maintenance of office and auxiliary rooms in basement, first and second floors.

For the maintenance of operating rooms No. 1, No. 2, the P2 system is provided, since these rooms have their own mode of operation - public service. If the operating mode for P1 system is constant and does not change during the day, then for P2 system - the mode is variable and depends on the number of people in the halls. In addition, the mode of operation of enterprise personnel may not coincide with the mode of public service .

The capacity of each supply and exhaust system is equal to the total air exchange respectively by inflow or by exhaust for all rooms serviced by this system.

Exhaust systems serve the same groups of rooms as the corresponding plenum, with the exception of individual rooms (bathrooms), from which a separate exhaust is arranged.

Air ducts are made of galvanized steel of rectangular section with gasket in space of suspended ceiling. Rectangular duct with width.

Air ducts are laid open in the basement, technical and utility rooms. In office rooms and operating rooms, air distribution is accepted "from top to top," that is, air supply is carried out in the upper zone with pouring jets down, exhaust - from the upper zone with concentrated jets.

Diagrams of air ducts wiring and air distributors arrangement in the Operating Rooms - air distribution is performed from the ceiling by fan jets in the direction of the working area through BETA four-sided distribution diffusers. Diffusers are usually located in the centers of squares or rectangles into which the room is divided. The diffuser is connected to the distribution air ducts by means of a box on the lower part of which the diffuser is attached, and the connection to the air ducts is made through a section of flexible air duct with a length of about 1.0 m., for the convenience of installation and attachment of the box for the diffuser. In addition, the flexible duct prevents the transmission of vibrations from the duct to the air distributor.

For other rooms inflow is performed through adjustable louver grilles (RAR). The number of grids is selected by the amount of supply air for each room separately and depending on the productivity of the grid, which is calculated from its living section.

Exhaust in the rooms is carried out through non-adjustable louver grilles (RAG) installed in the bottom of the exhaust air duct coinciding with the suspended ceiling. This duct is laid at the interior wall of the room. After the aerodynamic calculation, the plan displays duct sections and air terminal types.

4.5. Calculation of the air distribution.

Preselection of grilles and plafons is performed through air flow rate per grilles or plafon Lo and recommended air velocity in the flow section of grilles or plafon vop.

The vop value is about 1.5 m/s for plenum and 2 m/s for exhaust devices.

Flow Lo = L/N,

L - air exchange of the room respectively by inflow or by exhaust according to the Table of air exchange ,

N - number of plenum grids (plafons) or exhaust grids in the room

For operating room No. 2 Lo = 800/8 = 100 m3/hour

For operation room No. 1: Lo = 650/7 = 93 m3/hour

We calculate the estimated live section for air passage:

Then a grille or plafon with the nearest actual section ffact is selected from the catalog. For BETA air terminals the fact values are given in Table 4.3 below. and 4.4..

We accept ceiling diffusers with equal sides for the plenum system (P2) - SAD with dimensions of 300x300 mm for installation in operating rooms.

For the exhaust system - diffusers of rectangular shape RAG, dimensions 200x100 mm..

Appearance of diffuser grids, structure diagram is shown in images

A similar calculation and selection of air distribution diffusers (plafons) is made for the remaining rooms of the building.

4.5. Aerodynamic calculation of ducts.

The purpose of aerodynamic calculation is to determine the optimal design and section of air ducts, pressure losses in them with the condition that the air velocity should not exceed the recommended values.

In the premises of the building, rectangular air ducts made of galvanized sheet steel are provided, which are laid in the set ceiling.

Calculation procedure.

Calculation of P2 system.

1. P2 system diagram is divided into sections. Run - a line of duct with constant flow.

2. The velocity in the design area is determined approximately by the area of the duct section

, where

- speed in the design area,.

For 1 parcel

For 2 site

For 3 site

For 4 site

For 5 section

For section 6 and 7

3. On the approximate area the size of rectangular air ducts of AhB, mm is accepted. The dimensions of round and rectangular air ducts are accepted according to departmental construction standards VSN 35386 .

In this project, rectangular ducts:

For 1AcH = 0.2x0.2 = 0.04

For the 2nd site of AhV =0.2х0.2 = 0.04

For the 3rd site of AhV =0.2х0.2 = 0.04

For the 4th site of AhV =0.2х0.2 = 0.04

For 5 section AhB = 0, 3x0.2 = 0.06

For the 6th site of AhV =0.3х0.2 = 0.06

For the 7th site of AhV =0.3х0.2 = 0.06

4. The actual air velocity in the area is determined.

, m/s

For 1path = 0.7 m/s

For 2 section = 1.4 m/s

For 3 section = 2.8 m/s

For 4 section = 4.2 m/s

For 5path = 3.7m/sec

For 6 section = 6.9 m/s

For 7 section = 7.7 m/s

5. Pressure losses in the duct section are determined by the formula:

P = Rl + Z, Pa, where

R - specific pressure losses in the area, Pa/m

L - length of section, m

Z - pressure loss in local resistances, Pa

According to Table 22.15 of the Designer's Handbook "Internal Sanitary and Technical Devices," Part 3, Part 2, Chapter 22, there are specific pressure losses for friction R, Pa/m, in sections of the main branch.

Multiplying R by the length of the section determines the pressure loss by friction throughout the section.

6. In the areas we determine the coefficients of local resistances and find pressure losses on local resistances,

- the sum of local resistance coefficients on the site.

Values ​ ​ of some local resistances.

7. Total pressure losses at the site are determined

8. Total pressure losses in the direction are determined

9. Branches are calculated in the same way. Pressure losses in common parallel sections of the main direction and branches Rotv and Rmag.par. shall be linked to maximum error.

If the failure is more than 10%, a diaphragm or control flap shall be installed in accordance with Table 2.48 (Internal sanitary devices, Part 3, Part 2).

Calculation of local resistances of P2 system.

Section 1

Adjustable multi-pattern round section (SAD) plafone: = 1.4

Discharge 90 of stamped round section: = 0.21

= 1,61

Section 2

Tee to pass L0/Lc = 0.5 fp/fc = 0.8: = 0.4

= 0,4

Section 3

Tee to pass L0/Lc = 0.7 fp/fc = 0.8: = 1.55

= 1,55

Section 4

Tee to pass L0/Lc = 0.7 fp/fc = 0.8: = 1.55

= 1,55

Section 5

Tee to pass L0/Lc = 0.7 fp/fc = 0.8: = 1.55

Discharge 90 of stamped round section: = 0.21

= 1,76

Section 6

Tee for spreading L0/Lc = 0.6 fp/fc = 0.8: = 0.7

Section 7

Tee to pass L0/Lc = 0.7 fp/fc = 0.9: = 1.73

= 1,73

Site 8

Adjustable multi-diffuser round section plafone (SAD): = 1.4

Branch 90o = 0.25

= 1,65

Plot 9

Tee to pass L0/Lc = 0.7 fp/fc = 0.9: = 1.73

Branch 90o = 0.65

= 2,38

Site 10

Branch 90o = 0.50

Tee to pass L0/Lc = 0.7 fp/fc = 0.8: = 1.55

= 2,05

Site 11

Tee to pass L0/Lc = 0.7 fp/fc = 0.8: = 1.55

= 1,55

Section 12

Tee to pass L0/Lc = 0.7 fp/fc = 0.9: = 1.32

Branch 90o = 0.65

= 1,97

The non-binding of the two branches is 1.7% at a rate of 10%.

It is possible to install a diaphragm on a secondary branch to repay the misalignment.

Aerodynamic calculation of air ducts of exhaust ventilation system is similar to calculation of plenum system.

Then we carry out hydraulic calculation of B1 system .

The diagram of system B1 is divided into sections and then, according to the previously calculated speed, the dimensions of the ducts in the section are selected. We summarize all calculations into an aerodynamic calculation table.

Calculation of local resistances of B1 system.

Section 1

Non-adjustable grille (RAG): = 1,2

Discharge 90 of stamped round section: = 0.21, n = 4 pcs

= 2,04

Section 2

Tee to pass L0/Lc = 0.6 fp/fc = 1: = 0.4

= 0,4

Section 3

Tee to pass L0/Lc = 0.6 fp/fc = 0.8: = 1.55

= 1,55

Section 4

Tee to pass L0/Lc = 0.7 fp/fc = 1: = 1.32

= 1,32

Section 5

Tee to pass L0/Lc = 0.7 fp/fc = 0.8: = 1.55

Discharge 90 of stamped round section: = 0.21

= 1,76

Section 6

Tee for spreading L0/Lc = 0.6 fp/fc = 0.8: = 0.7

Section 7

Tee to pass L0/Lc = 0.7 fp/fc = 0.9: = 1.73

= 1,73

Site 8

Tee to pass L0/Lc = 0.7 fp/fc = 0.9: = 1.73

Discharge 90 of stamped round section: = 0.55

= 2,28

With respect to the secondary branch (sections 9-18), the non-binding of the two branches is 9.5% at a norm of 10%.

It is possible to install a diaphragm on a secondary branch to repay the misalignment.

Aerodynamic calculations are given in Appendix No. 13 to this Explanatory Note.

Note: calculations are carried out in Excel, according to specially developed formulas and nested tables with reference data. Development of the design institute of Almaty.

Similarly, we calculate the remaining branches of system B1, as well as supply and exhaust systems P1, B2 - B5.

All branches on ventilation systems are provided with control valves for installation adjustment during commissioning.

4.7. Selection of main equipment and design of plenum and exhaust plants.

In accordance with the Terms of Reference (refer to Initial data, para. 1.5. Explanatory Note) central ventilation and air conditioning equipment shall be manufactured by Carrier (USA).

Selection of the central air conditioner is carried out according to the air flow rate and total pressure equal to the sum of aerodynamic resistances of its individual units and ventilation network.

Selection is carried out according to the characteristics of fans given in the catalogs of manufacturers. Aerodynamic resistance of ventilation network is determined as a result of aerodynamic calculation .

Aerodynamic resistance of functional units of central conditioner is determined during their calculation or by tables of corresponding catalogue.

In this project - according to the characteristics provided by the manufacturer - Carrier (USA ).

4.7.1. Plenum unit P-1.

The operating air flow ranges for different types of air conditioners are determined by the allowable speed values in the flow sections of the blocks, the available areas for their placement, the noise level and other factors.

Selection of the air conditioner size is carried out (according to the catalog) by air capacity L = 9720 m3/h in accordance with the task compiled for selection of units and control boards for them.

The task is shown in the graphic part of the project, Sheet 12.

Select type 39HQ 09.06

Carrier 39HQ air conditioners are a modular design, each component of which can be optimized to provide the required performance. The air conditioner includes high-quality components such as filters, heat recovery systems, fans, cooling and heating heat exchangers, humidifiers and silencers. Thanks to this - high air quality due to filters of various degrees of purification, high efficiency of heat recovery systems, reduction of energy consumption required for heating, cooling and humidification,

The design of the air conditioner is shown in Figure 4.7. and working drawings of the graphic part of the project, Sheet 12.

DESIGNATIONS:

1. Frame of profiled steel with corners and central posts.

2. Heat insulated panels 60 mm thick.

3. Rigid support frame of galvanized profile.

4. Condensate collection tray in outdoor air intake section (stainless steel).

5. Filter elements installed in stainless steel frames.

6. Special corrosion resistant coating.

7. Inner and outer walls of polyester coated steel panels.

8. Air coolers, on aluminum frame with built-in stainless steel trays and plastic drop separators.

9. Special panel and frame design to prevent condensate falling out.

10. Devices for monitoring the condition of devices and doors for maintenance.

11. Smooth interior surfaces.

12. Access to removable filters.

13. Condensate collection tray with drain pipe in outdoor air intake section and filter section.

14. Inclined tray for condensate collection and removal.

15. Access to a removable drop separator located behind the air cooler.

16. Unattended motor bearing fans.

17. Fans (extend laterally).

18. Special rotors of sorption recuperator for optimal heat and moisture utilization.

19. Low noise radial fans, on vibration isolating supports.

20. Aluminium air valves with twin nylon bearings.

21. Plate silencers.

22. Highly efficient belt drive.

Selection of air intake unit.

Air intake units are used for reception, regulation, mixing and distribution of the volume of air (external and recirculation) supplied to the air conditioner along the living section.

Aerodynamic resistance of the receiving unit at nominal capacity of the conditioner is not more than 70 Pa. Air valves are designed to control the volumes of external and recirculation air entering the air conditioner.

All valves are made according to a single structural scheme and consist of a body and rotary blades, single in section for valves of all sizes.

Selection is carried out according to the selected standard size of the air conditioner in accordance with the task. We accept the unit with vertical valve for installation.

The aerodynamic drag of the valve is determined depending on V = 3 m/s, and in this case is, ΔPkl = 5 Pa. Valve dimensions 1378 x 898 mm. Besides, inlet section is equipped with flexible device to prevent transmission of vibration of plenum plant to construction structures.

Selection of filter section.

In civilian buildings, it is recommended to use double dust cleaning - sleeve filters and cell filters for cleaning air from dust. Filters are installed in special panels providing their removal and re-installation during regeneration. Selection of filters is carried out in accordance with the recommendations of the equipment manufacturer.

This project provides for double air cleaning

In the first stage, cleaning class G4.

In the second stage, cleaning class F7. When constructing the plenum unit, attention should be paid to the free space from the side of the filter maintenance in order to be able to roll out the filter section when cleaning the filter.

Data for selection: volume of supplied air L = 9720m3/h.

Filtering class: G4, F4/

Initial dynamic resistance of filters as per manufacturer data - ΔRn 252 AP.

Final aerodynamic drag: ΔPk = 336Pa .

Upon reaching this resistance, a signal is sent to the control panel or to the control room about the need to clean the filter.

Selection of heat recovery unit.

In this design, Carrier heat-recovery equipment is used to dispose of exhaust heat in a rotary recuperator consisting of a rotating rotor, part of which is installed in the exhaust air flow, and the lower part in the supply air flow. When the rotor passes through the exhaust air zone, heat is transferred to the rotor from the removed air, and when the rotor passes in the plenum air zone, heat is transferred to the external air.

Due to the high rotation speed of the rotor, there is no overflow of external supply air and exhaust removed air. The efficiency factor of the rotor heat exchanger is 8590%. At outdoor temperature of 17 ° С, after passing through the recuperator, the plenum air temperature will be + 6.9 ° С according to the plant. That is, in the water heater it will be necessary to warm the air from this temperature to 22 ° C

Calorifer calculation - superheater.

The operating parameters of this heater are designed to heat the supply air after the heat exchanger.

In this case it is required to dogrevat air from temperature of 6.9 wasps to +22os, but it is more expedient to pick up the heater calculated on full load as in case of failure of the block of heatutilization a heater - the dogrevatel will have to compensate missing loading.

We accept the water heater for the installation.

Data for matching:

• air flow L = 9720 m3/h;

• temperature of the heated tn air = 17 wasps, tpr = 22 wasps;

• heat carrier parameters τг = 95 wasps; τо = 70 wasps.

Calculation sequence:

1. Determine the amount of heat required to heat the air:

2. We determine the coolant flow rate:

3. We determine the actual mass air velocity in the front section of the air conditioner:

3. We determine the speed of water movement in the tubes:

4. We calculate the heat transfer coefficient of the heater:

6. We determine the required heating area of the heater:

7. We define the number of rows:

Aerodynamic resistance of the heater is determined depending on

We calculate the hydraulic resistance of the heater by water:

Selection of fan and type of motor.

The selection of the fan is made according to its characteristics.

Fan capacity (air flow rate) Lvent, m3/h, we take in proportion to the calculated air flow rate for the system:

It is recommended to select the fan considering that in the operating mode its efficiency should differ from the maximum possible by no more than 10%.

Select the RDH E4 fan (Nicotra manufacturer).

- Impeller diameter D = 400 mm

- Number of blades - 11,

- Pressure: up to 3500 Pa

- Impeller speed: n = 2240 minˉ¹

- Full Efficiency:? = 78%

- Sound power level: Lp∑ = 88dB

- Output speed: V = 10.1 m/s

The required power on the motor shaft is determined by the formula:

Installation power of electric motor is determined by formula

Characteristics of RDH E fans:

4.8. Construction of air treatment processes on the I-D diagram for the Operating Rooms.

Warm Year Baseline:

- Number of people in room 60;

- barometric pressure 101325 Pa;

- the length of the room is 24m;

- the width of the room is 15 m;

- room height 3.0 m;

- height of ventilation holes is 2.8 m;

- ambient air temperature 33.6 С;

- external air enthalpy 66.5 kJ/kg;

- internal air temperature 25 С;

- internal air humidity 60%;

- heat input into the room without taking into account people 3669 kJ/kg;

- heat input to the room from people 649 kJ/kg;

- water release into the premises without taking into account people 0;

- moisture release into the room from people 4.06 kg/h;

- air supply to rooms 1420 m3/h;

- cold water temperature 7 С;

- temperature gradient, according to the results of intermediate calculation (∆Qya/V=50 kJ/( m3∙ch)) 0.4 S/m.

The results of the process construction are presented in the graphical part of the Project.

The warm season air treatment consists of the following processes:

ON - preliminary cooling of air in the recuperator

AO - air cooling in air cooler;

OP - air heating in fan and supply air duct;

LDP - indoor process.

Cold Year Baseline:

- ambient air temperature 17 С;

- external air enthalpy 18.2 kJ/kg;

- internal air temperature 20 С;

- internal air humidity 40%;

- heat input into the room without taking into account people 1406.0 kJ/kg;

- heat input to the room from people 1010kJ/kg;

- water release into the premises without taking into account people 0;

- moisture release into the room from people 2.34 kg/h;

- temperature gradient, according to the results of intermediate calculation (∆Qya/V=56,1 kJ/( m3∙ch)) 0.4 S/m.

The results of the process are shown in the graphic part of the project.

Air treatment during the cold season consists of the following processes:

NZ -K - pre-heating in recuperator

NC - air heating in the air heater;

MO - air cooling in air ducts

HVAC - indoor processes

4.9. Smoke activities.

In accordance with paragraphs 8.1 and 8.2 of SNiP 41012003 "Heating. Ventilation. Air conditioning, "smoke ventilation systems of buildings should be provided to ensure safe evacuation and rescue of people from the building in case of fire in one of the rooms. Smoke ventilation systems shall be autonomous for each fire compartment .

Exhaust smoke ventilation systems for removal of combustion products in case of fire shall include:

a) from corridors and halls of residential, public, administrative-domestic and multifunctional buildings with a height of more than 28 m. The height of the building is determined by the difference in elevations of the fare surface for fire vehicles and the lower elevation of the opening window (opening) in the outer wall of the upper floor (not counting the upper technical);

b) from the corridors (tunnels) of the basement and basement floors of residential, public, administrative, industrial and multifunctional buildings when exiting these corridors from premises intended for the permanent stay of people (regardless of the number of people in these premises);

c) of corridors more than 15 m long without natural lighting of buildings with two or more floors (except for the first floors of the building ):

production and storage categories A, B and B;

public and multifunctional;

d) from common corridors and halls of buildings for various purposes with non-smokable staircases;

e) from atriums and passages;

f) from each production or storage room with permanent workplaces without natural lighting or with natural lighting through windows and lights that do not have mechanized drives for opening framugs in windows (at a level of 2.2 m and higher from the floor to the bottom of the framugas) and openings in lanterns (in both cases, area sufficient to remove smoke in case of fire)if the premises are classified in categories A, B, B1B3, as well as B4, D or D in buildings of IV degree of fire resistance;

g) dressing rooms with an area of ​ ​ 200 m2 or more;

and) from each room without natural light or with natural light through windows or lights that do not have mechanized actuators for opening the frame of windows and openings in lights, the area is insufficient to remove smoke in case of fire:

- social, designed for the mass stay of people;

- 50 m2 or more with permanent workplaces intended for the storage or use of combustible substances and materials, as well as libraries, book repositories, archives, paper warehouses;

- store trading rooms;

c) from premises for storage of cars of closed above-ground and underground car parks, as well as from isolated ramps of these car parks .

It is allowed to design the removal of combustion products through the adjacent corridor from rooms with an area of ​ ​ up to 200 m2.

In the building in the basement (basement) there is a corridor with a length of more than 15 m, which does not have natural light. Adjoining rooms with area less than 200 m2.

No smoke exhaust system is provided on the ground floor. All rooms have window openings. Window openings have sufficient area for smoke removal in case of fire. According to SNiP 41012003 "Heating, ventilation and air conditioning" from corridors more than 15 m long, a smoke ventilation system is provided in buildings on two floors or more, except for the first floors of the building.

There is no corridor on the second floor, and all rooms have window openings in the outer walls. Window openings have a sufficient area to remove smoke in a fire, that is, a smoke ventilation system is also not required.

Thus, in the event of a fire, the project provides for a smoke exhaust ventilation system - VD1, from the corridor of the basement (basement), which includes:

1. Smoke removal valves:

2. Smoke removal fans;

3. Smoke removal ducts to remove smoke from corridors.

Exhaust smoke ventilation systems designed to protect corridors should be designed separately from systems designed to protect premises.

General systems for protection of premises of various functional fire hazard are not allowed.

When removing combustion products from corridors, smoke receptacles should be placed in shafts under the ceiling of the corridor, but not below the top level of the doorway. It is allowed to install smoke receiving devices on branches to smoke shafts. The length of the corridor served by one smoke receiver shall not exceed 45 m.

The calculation of the consumption of removed combustion products is determined in accordance with the recommendations of Manual 4.91 to SNiP 2.08.0991 "Smoke protection in case of fire." The smoke consumption (kg/h) to be removed from the corridor or hall should be determined for public, administrative and industrial buildings.

The calculation results are given in the table in Appendix No. 14 to this Explanatory Note "Calculation of smoke protection."

According to the calculation results:

The pressure loss for which power is to be calculated is 418 Pa for the fan.

Total gas flow rate GO = 4.24 kg/s.

Fan Performance:

Fan speed is determined by capacity and conditional pressure.

According to these parameters, a roof radial smoke removal fan with emission to the sides of VKRS10DU is selected, which is designed to remove high-temperature smoke-air mixtures arising during a fire and simultaneously remove heat from the building premises.

VKRSDU fan is used in emergency exhaust ventilation systems of industrial, public, residential, administrative and other premises, and is intended for installation on roofs of buildings and structures and is intended for use in the open air.

Fire-fighting normally closed valves of KPU1K grade with fire resistance limits EI 120 are adopted as smoke removal valves.

Fire-fighting valves shall not be installed for systems serving one room or one stairwell, one stairwell or one elevator shaft.

The project in the corridor provides for two smoke removal zones and, accordingly, two valves are installed.

At the points of connection to the system, the air ducts are covered with a fire-retardant coating of the UZSMV type with fire resistance of 0.5 hour. KPU1 smoke valves are provided with automatic, remote and manual control.

The smoke ventilation system is switched on automatically and remotely when the fire alarm is triggered.

Smoke release into the atmosphere at a height of not less than 2 m from the roof, in accordance with item 8.10

Air ducts of smoke ventilation are made of class II steel, = 1.5 mm on welding, to ensure the fire resistance required in accordance with item 8.10 of 0.5 h. Brickwork = 65 mm is also used for this purpose .

In the premises of the server Data Processing Center in the basement, there is a gas fire extinguishing, an autonomous emergency exhaust unit, which is switched on after the gas fire extinguishing operation and removes gases and smoke after the fire is provided by the PT brand.

4.10. Noise silencing activities.

To combat noise from ventilation units and reduce it to the level of normalized value, the following measures are provided:

- installation of fan units on vibration isolating bases;

- connection of air ducts with fans is carried out using flexible inserts;

- installation of silencers;

- arrangement of ventilation units in specially enclosed rooms, ventilation chambers;

• sound insulation of enclosing structures of ventilation chambers rooms;

• compliance of plant operation parameters with optimal values for this type and size, as well as design requirements;

• timely inspection, maintenance, repair and replacement of worn-out plant parts by specialized operation services.

4.9.1. Calculation of P2 silencer.

The source of aerodynamic noise transmitted to the room through air ducts is a ventilation unit.

The sound pressure level, dB, depends on the air supply, m ³/s, and the pressure developed by the fan, Pa.

The noise level allowed depends on the type of room. In the ventilation network, the sound pressure is suppressed along the length, when the cross section of the duct changes, in turns and tees (branches) and is reflected from the open end of the duct or grid installed at the inlet.

Calculation is carried out on eight average geometric frequencies of octave fields (63,125,250,500,1000,2000,4000,8000 Hz).

Sound pressure is dispersed in the room, the value of which is not taken into account for most rooms of civilian buildings.

The design direction is the shortest path through the duct network from the ventilation unit to the nearest air distributor or grid.

Losses in silencers should be equal to the remainder of the subtraction from the sound power of the fan of losses in the ducts and the value of the permissible noise level in the room.

Calculation is made in accordance with Chapter 12, Designer's Handbook, Internal Sanitary Devices, Part 3, Part 1, as well as SNI1277 "Noise Protection."

1. The octave levels of sound power of the fan (according to its data) are determined: 2. The octave level of sound noise power generated by the air distribution grid in the hall is detected, determined by the formula:

3. The total reduction of sound power level along the noise propagation path in the plenum duct is found by the formula

We determine the free section area of the silencer by the formula :

Q - volumetric air flow through the silencer, m3/s;

vdop - permissible air speed in the silencer, m/s.

When installing a silencer in the system serving the operating rooms (La - up to 55dB) - it is taken equal to 10 m/s.

Then:

Fgl = 2.7/10 = 0.27 m2.

Select the 5.90407 GTR plate silencer with a section length of 1000 mm and an internal size of 300x200.

Required number of silencers for each octave band:

In this way, we install one noise silencer of gtr series 5.90407 of rectangular section.

Section 5

Cold supply

5.1. Cold supply of air conditioning system.

Equipment of ventilation systems, air conditioning systems, cold supply systems is located in the building in the technical rooms and the ventilation chamber of the basement at elevation 3,000.

The plenum unit P1, in order to ensure the possibility of heat utilization, works together with the exhaust unit B1 and organizes inflow in regulated volumes in the administrative part of the building.

Heat recovery is provided using a system using a rotary recuperator, in which the exhaust air heat is partially disposed of. The final overheating of the plenum, as well as its cooling in the warm period of the year, is provided by independent heat exchangers for heating and cooling the plenum air.. The required set of functions of P1 installation in the cold period of the year includes:

- cleaning of supply air in filters,

- heating of supply air in the rotary heat recovery recuperator,

- heating of supply air in heating heater.

In the warm season:

- cleaning of supply air in filters,

- cooling in the calorifer of the cold supply system.

The required set of functions of B1 installation in the cold period of the year includes:

- provision of exhaust air heat utilization by the designed system,

- provision of head in the network by means of ventilation plant,

In the warm period:

- provision of exhaust air cold utilization by means of rotary recuperator.

In addition, fancoyles are installed in office and operating rooms, which work in two modes - in winter - with air heaters, and in summer with air coolers.

The source of cold for the operation of air conditioners and funcoils in the summer is an air cooling refrigerator installed outside the building on the foundation.

The project provides for the use of Carrier ventilation equipment widely represented on the modern Russian market and the refrigeration machine of the same company.

WILO Freezing Protection Pump (Germany) is provided to ensure coolant circulation in the external air heater circuit during the transition period.

The cold supply automation system provides for the use of Carrier's ProDialog Plus controller.

The controller has 4 universal inputs (configurable for different types of sensors), 4 inputs for temperature sensors, 4 relay inputs, 4 relay outputs and 4 analog outputs. Expansion units are also provided separately for digital (4 inputs and outputs) and for analog (8 inputs and 2 outputs) communication channels. Use the operator panel to change the parameters. The controller uses software from the same firm.

Air performance of designed systems:

P1 9720 m3/h system,

P21500 m3/h system.

The cold demand of these systems is determined by the formula:

, W,

where:

Sv-ha - air heat capacity, w/m3grad,

Gfa - mass air flow rate, kg/h

Shopping mall - the reference temperature of air, design temperature of external air of the summer period, 31.5 wasps

Ton - temperature of incoming air, 22 wasps

For P1

Qchol = 0.28 • 1,005 • 1.22 • • 9720 • (31,522) = 31700 w

For P2

Qchol = 0.28 • 1,005 • 1.22 • • 1500 • (31,522) = 4730 w

Total demand for cold supply systems is 36430 watts,

Their calculation of heat inputs (Appendix No. 10 to the Explanatory Note), the maximum cold consumption in the fancoyl cold supply system is 121700W.

Given the uneven consumption of cold by fancoyles, which consume less cold in the estimated hour - depending on the location of the sun in the morning, maximum heat emissions on the eastern side, in the afternoon - on the western side. We accept the estimated heat input of 80% of the maximum. Total = 121700x0.8 = 97360 w

The total cold demand will be 97360 + 36430 = 133790W.

Upon request, the manufacturer (according to the equipment catalog) was selected a chiller with air-cooled condenser model 30RBS160, with a hydraulic module, a cooling capacity of 144.3 KW.

Technical specifications of the chiller:

- Number of refrigeration circuits - 2,

- Number of compressors - 4,

- Number of condenser fans - 2,

- Weight without hydraulic module - 1046 kg.,

- The sizes (DHSHKHV) - 2258х2050х1330 mm.,

- Hydraulic module - with twin high pressure pump.

- Maximum electric power consumption - 71.5 kW

- Refrigerant - Freon of group R410A

Hydromodule.

Built-in hydraulic module with two high-pressure centrifugal pumps with pump operating time equalization and automatic switching to standby pump in case of failure.

The pressure measurement system using two pressure sensors indicates the water flow rate, water pressure and insufficient water volume in the system.

The appearance and design of the hydraulic module is shown in Figure 5.2.

The water filter protects the water pump from dirt circulating in the system.

Membrane expansion tank of sufficient capacity to ensure water circuit tightness.

Designations

1. Heat exchanger outlet/inlet pressure gauges and blowdown valves

2. Plate heat exchanger (evaporator)

3. Insulation coating against freezing

4. Safety valve

5. Screen filter

6. Water inlet (return from unit)

7. Water outlet (supply to unit)

8. Water flow control float valve

9. Water Flow Switch

10. Expansion tank

11. Water pump

5.2 Description of the schematic diagram of cold supply.

A two-circuit closed cold supply scheme is provided, using an air-cooled refrigerator condenser Freon group R410A. The second one passes through evaporator (condenser) of refrigerating machine, system of pipelines and heating group. Filling of this circuit is provided with water.

The new generation of AquaSnap refrigeration machines equipped with an air-cooled condenser are designed and manufactured in accordance with modern environmental requirements for working with the new R410A refrigerant and are equipped with spiral compressors, low-noise fans made of a special composite material and a microprocessor control system. These refrigeration machines are equipped with a built-in hydraulic module as a standard, which greatly simplifies the connection to the main power supply network, the supply of cooled and return water.

The algorithm of the electronic control system ensures optimal operation of the compressor, eliminates the need for an expansion tank plate heat exchangers with aluminum plates and copper tubes. The type and size of the condenser and evaporator heat exchangers are the same, since in different periods of the year these devices perform interchangeable functions. This is primarily due to the specifics of the plant operation in various modes. Mode selection is performed by built-in four-way valve.

In the supply air (TC) cooling mode, refrigerant vapors from the compressor outlet valve are directed by a four-way valve to the secondary circuit heat exchanger, where they are condensed. Through the check valve, bypassing the first thermostatic valve along the bypass line, the liquid freon under high pressure enters the receiver, and then is sent to the second thermostatic valve (TFV). After TPP, refrigerant is supplied to the heat exchanger of the third cold supply circuit, where it is evaporated by cooling the secondary coolant (water), which, in turn, cools the supply air in the heating group of the ventilation plant.

The built-in hydraulic module eliminates the need for an on-site pump and does not require additional space. The module has all the necessary components to ensure the optimal operation of the system: a removable screen filter, a high-pressure water pump, an expansion tank, a water flow switch, pressure gauges, a safety valve.

The control valve ensures optimum water flow according to the plant characteristics.

The new R410A ozone-safe refrigerant meets all international requirements, has the same properties and guaranteed reliability as R22, completely replacing it in low and medium capacity air conditioning systems. The R410A refrigerant has been tested at Carrier plants.

Among the most important features of this machine that determine its choice, the following can be distinguished:

• four-way cycle reversal valve;

• reinforced design of heat exchangers, since in heating mode the heat exchanger of the third circuit operates at relatively high pressure;

• a liquid separator is installed in front of the compressor to prevent liquid coolant from entering the compressor and to avoid hydraulic shock;

• there are two sets of TRV and set of check valves;

• on the compressor connection pipes there are receivers and separators, one on each line.

5.3. Protection against icing of system elements.

The most likely is the formation of an ice fur coat on the finning of the tubes of the caliber group of the exhaust plant with long-term operation under conditions of low external temperatures. Icing of system elements in some cases leads to deterioration of heat engineering efficiency of heat exchange devices and to deterioration of ventilation equipment operation due to increase in values of aerodynamic resistance of calorifer group devices. To prevent such cases, the system provides an algorithm for defrosting the system. Several programs are included in the control program of the ProDialog Plus automation system. In all programs, the initial data for analyzing the condition of the heat exchanger of the external unit is room temperature, external temperature and air temperature at the outlet of the plenum unit.

To prevent false unfreezing in all programs, the total operating time of the compressor is measured from the moment the heating mode is switched on for the current day and from the moment the previous defreezing cycle ends. The plant operation modes are controlled by automatic switching of the position of the four-way cycle reversal valve. The most important point in this case is the continuity of operation of the compressor, since the increase in the number of starts negatively affects its technical condition. Moreover, the life of the compressor directly depends on the number of stops and subsequent starts. The design of the selected refrigerator and the possibility of flexible adjustment of the automation system allow you to organize a defrosting algorithm with the least wear and tear of the equipment.

As a rule, one of the defrosting programs is a preventive defrosting program (type A defrosting), and the other is the main one (type C defrosting). Programs differ in compressor operating time, defrost cycle duration and corresponding temperature difference. Defrosting is activated when all conditions stipulated by the program algorithm are unambiguously observed. As an example of such conditions, conditions can be mentioned when after 70 minutes of operation of the compressor, it is supposed to begin monitoring the condition of the heat exchanger of the external unit according to defrosting parameters of type C. If no critical conditions are detected (approx.: the pressure drop in the caliber group did not exceed the value 1.5 times higher than the nominal), then the system continues to work, and automation constantly monitors the need for defrosting. If in 120 minutes of total operating time of the compressor there is no need for defrosting, then the system switches to preventive control mode for defrosting parameters by type A. Since defrosting parameters by type A are less rigid than defrosting parameters by type C, then, if necessary, the defrosting mode will be turned on at the initial moment of icing for a short time.

Thus, the defrosting mode of type C, which is a kind of emergency mode, can be implemented only at the beginning of the plant's operation, when the operating conditions have not yet been fully identified by the system.

The 30RBS160 chillers use second-generation Flying Bird fans, which used the latest corporate aircraft technology.

Fans are made of special composite material and have shaped blades. The statically and dynamically balanced wheel is attached directly to the engine shaft, which allows you to optimize the sound qualities of the fan and get rid of the noise peak at low frequencies. In case of partial loading or low ambient temperature, the fan motor is automatically switched to low speed.

In these refrigeration machines, the fan tower arrangement is used, i.e. the fan is not fixed on the top panel, but on a special super-rigid tower base having a vibration damping structure. This layout solution made it possible to significantly reduce the level of noise, and also excluded the possibility of transmitting vibrations to the housing and external panels of the installation.

The evaporator has welded joints, is a steel plate heat exchanger, is designed to maximize the thermodynamic properties of the R407C refrigerant, provides optimization of technical characteristics, as well as low hydraulic resistance on the side of the water circuit.

In the chiller 30RA160, the evaporator has a double cooling circuit. The unit is equipped with frost protection by means of a heater on the evaporator in case of disengagement of the evaporator. The refrigeration circuit is fully sealed. All piping and loop components have welded connections. Capillary tubes - as a possible possible cause of leakage - have been replaced. The pressure switches are replaced with pressure sensors mounted directly to the piping.

Pro-Dialog Plus is an intelligent microprocessor control system that combines precision and unique ease of control. The ProDialog Plus system monitors all operating parameters of the plant, optimizing the operation of compressors, fans, reversing valve and water pump.

To reduce power consumption, ProDialog Plus automatically sets the temperature of the cooled water to the ambient temperature or return water, or uses two installation points. The ProDialog Plus self-adapting control system guarantees full protection of compressors.

The system constantly optimizes the compressor operation time according to the specified characteristics, preventing unnecessary restarts.

The easy-to-use ProDialog Plus control system has an easy-to-use control panel with a cooling circuit diagram on it with control buttons at its various points and a digital display. Modular electronic monitoring units with diagnostics on the LED, allowing you to determine the parameters of the installation at any point.

Indicators, display, buttons are located on the schematic image of the machine. The user can immediately find out all operating parameters: pressure, temperature, operating time, etc.

Among the advantages of this thawing scheme are the following:

• flexibility of automation system settings due to application of perfect control device;

• no major additional investment in the system;

• energy, electrical and thermal savings;

• full realization of the capabilities of the selected equipment;

• Use in the system of the most common typical catalogue items of manufacturers representing their products in the construction region;

• possibility of system improvement and modernization during operation and repair due to new requirements of the building owner (possibility to reduce defrost time);

• increase of reliability and service life of equipment, in particular compressor of refrigerating machine.

5.3. Cold supply of fancoyles. Hydraulic calculation.

The fancoyl cold supply system is adopted as horizontal, double-tube with associated motion for the coolant circuit and coolant circuit.

Cooling of funcoils is provided from distribution and collection headers of control unit No. 2.

Connection of fan coils to the main pipelines of heat supply and cold supply circuits is carried out both on the supply and on the return pipeline through the ball and coupling valve. On the supply pipeline, after the ball valve, a three-way control valve is connected, which is supplied with a funcoil.

Floor pipelines of these systems are laid closed in the floor structure of the serviced floor with installation of panels in the floor for maintenance of control valves.

Hydraulic calculation of the fancoyl cold supply system is carried out in the same way as the fancoyl heat supply system (Appendix No. 5 to the Explanatory Note).

All calculations are summarized in tabular form in Appendix 15 to the Explanatory Note "Hydraulic Calculation of the Fancoil Cold Supply System."

The difference in this system is that the difference in the temperature of the supply and return water is 5 ° C, which leads to a significant increase in the flow rate of the coolant in the sections, and therefore to increases in the diameters of the calculated sections. Balancing of cold supply system branches is also performed by Danfoss ABQM automatic balancing valves.

Section 6

Data Center Precision Conditioning System

6.1. Calculation of required cooling capacity and number of PCIS air conditioners.

Heat input from process equipment is taken as the main values of heat input in the server room.

Third-party heat sources (heat supply through external fences, openings, ventilation, from lighting sources, people) are unstable and have small values ​ ​ in relation to heat generation installed in server equipment, then they can be neglected.

The list of equipment to be installed, the size occupied in the server and telecommunication rack and the maximum heat generation (according to the manufacturer) are presented in Appendix 16 to the Explanatory Note.

Thus:

The total number of server and telecommunication racks, which allows to place the layout and area of the room is 18 pcs. (or 756U).

The rated number of racks with installed equipment will be 12.4 racks (or 519U).

The design heat generation of the installed equipment is 202.3 kW.

The nominal (design) amount of free space for installation of server and telecommunication equipment will be 5.6 racks (237 U).

Considering that the average design heat generation of one rack is 16.4 kW, a cooling capacity margin of 5.6 • 16.4 = 92.4 kW will be required.

The required cooling capacity of PCIS ≈ 295 kW.

6.2. Technological and design solutions adopted.

In accordance with the Engineering Specification, the Project provides for precision conditioning of the machine room (Server) of the Data Processing Center.

The Server room is located in the basement in the axes AG/12.

The Precision Air Conditioning System shall provide optimum temperature and humidity conditions for switching, telecommunication, server, electrical and other process equipment located in the Server Room.

Air conditioners shall provide air circulation according to the principle of organization of cold and hot corridors by air circulation method at the level of telecommunication and server cabinets, and ensure uniform distribution of air conditioned air into the inter-row space.

This principle is shown in Figure 6.1 below.

The design solution in the server room for assimilation of heat from process equipment is the inter-row air conditioners of the company "Stulz" (Germany) of the CRS361AS type CyberRow system.

The location of the internal air conditioning modules ensures the presence of "cold" and "hot" air corridors.

Air conditioners maintain the specified temperature and relative humidity level.

CyberRow is an advanced precision air conditioner manufactured to meet the cooling needs of the racks. In air conditioning

CyberRow innovative air supply system is optimized due to modern technology that increases its productivity, adaptability and efficiency.

In CyberRow, a new direction of air supply is implemented - in the horizontal plane. Air conditioners are located in the server room itself, between the racks, which allows them to remove a significant amount of heat generated by the servers from the servers. This technique significantly improves air flows, since cold air flows in two directions through the side holes and is evenly distributed throughout the information center.

Due to the horizontal air outlets in two directions, the air conditioner CyberRow creates a uniform air flow close to the posts, concentrated in the front of the posts. Thus, cold air is always directed where it is needed.

The location of the air conditioners in the immediate vicinity of the racks is a short distance away, so that the cold and warm air mix little with each other. This contributes to the high efficiency of the CyberRow system.

The electronic control system monitors and controls all components inside and outside the air conditioner required to create

cold air flow.

Independent ECS fans with stepless adjustment provide maximum efficiency

The continuous adjustment of the compressor provides precision cooling capacity and a 50% reduction in power consumption during compressor start-up due to the smooth start-up function.

The electronic temperature control valve allows you to quickly (within a few seconds) change the cooling capacity.

The installed equipment complies with existing standards and GOST, is certified according to European standard DIN ISO 9001/EN 29001 and according to Russian standards GOST 12.2.02884, GOST 12.1.01290, GOST 12.1.00383.

air conditioner housing consists of self-supporting frame structure with removable facing panels and doors. All steel parts are protected against corrosion by means of special anticorrosive powder. Panels and doors have rubber seals.

Air conditioners cooling circuit consists of evaporator, electronic temperature control valve, EC compressor and external condenser with air cooling. When the air flow of the room supplied by the fans passes through the evaporator, heat is removed from the air and transferred to the refrigerant. Air conditioner and external condenser are connected to each other by closed coolant circuit.

Arrangement of PCS equipment:

the lower limit is limited by the operation of winter start-up units, the upper design temperature at which the conditioner will operate without reducing the cooling capacity and exceeding the threshold pressure in the system.

CRS361AS air conditioners are paired with air cooling condensers (external units of the PCIS system) of the KSV045A22 brand, manufactured by Stulz (Germany).

Between air conditioners and condensers there are routes of chladone pipelines and electric cable.

The air flow diagram in the server room is as follows:

air is sucked from the rear of the air conditioner from the "hot" corridor, and supply from the front to the cold corridor.

To improve the cooling efficiency of the equipment and prevent the flow of cooled air to the suction side of the air conditioner, it is recommended to isolate the "cold" corridor between K1K4 air conditioners.

The cooling capacity is controlled on AS air conditioners by means of the compressor drive and fan speed depending on the temperatures of the supplied and recirculated air.

The main component is the coolant circuit (with remote coil

condenser), which consists of a compressor, a liquid refrigerant receiver, a refrigerant filter, an electronic expansion valve and an evaporator. Air conditioners shall CyberRow be connected to the remote condenser to fully form this circuit and ensure the operation of the device.

The system functions as follows:

The compressor provides a higher temperature and a higher refrigerant pressure. Passing through the condenser, the hot gas is cooled and liquefied; heat generated at that is supplied to external air. When passing through the electronic expansion valve, pressure losses of the liquid refrigerant occur, and it is prepared for evaporation. Evaporation occurs in an evaporator where the refrigerant absorbs the heat of the internal hot air and accordingly cools the air.

The components of the circuit are connected to each other by welded copper pipes, due to which excellent tightness is guaranteed. Operating shut-off valves are located on the liquid line and hot gas line leading to the remote condenser.

The air conditioners use the R410A refrigerant (HFC).

All models use spiral compressors. The main components of the compressors are an electric motor and a mechanical part operating from this electric motor. They compress the gaseous refrigerant. In spiral compressors, the compression section consists of two snails; Note here that one snail is located inside the other. One snail is stationary, while the other snail is orbiting, sucking and compressing the gas.

The oil separator, which is installed on the hot gas side of the compressor, serves to recover oil in all operating states. Separated oil is injected on the suction side of the compressor.

The liquid refrigerant receiver, which is located between the condenser and the filter moisture separator, maintains the level of supercooling of the refrigerant constant and provides maximum efficiency under varying operating conditions.

The refrigerant delivery valve is installed behind the liquid refrigerant receiver as a safety device to protect against excessive pressure in the circuit, even when the conditioner is disconnected. Setup = 40 bar

The moisture separator filter is a combined mechanical and chemical filter that separates all moisture particles from the coolant that passes through it.

The electronic expansion valve is an electronically controlled device that controls the evaporation pressure inside the evaporator depending on the thermal load.

Evaporator is installed where heat is supplied from internal air to gaseous refrigerant. It is a coil with copper pipes and aluminum fins (designed for use only in corrosive and salt-free atmospheres).

Fans are radial, EC type (with electronic switching), with back-bent blades, which are made of galvanized sheet steel. The rotor is also made of galvanized sheet steel; it is installed in ball bearings and dynamically balanced in accordance with the requirements of DIN ISO1940, quality level G6.3. Protection class IP54. Insulation Class B.

The air conditioning scheme used in this facility is N + 1.

In case of failure of one working air conditioner, with insufficient cooling power of the working air conditioner, the standby air conditioner is switched on. For equal generation of air conditioners reserve, a sequencing function is provided (switching of air conditioners from the state of operation to the reserve).

To start the air conditioner in the cold season, a winter start-up system is provided, with an increased volume of liquid linear receiver.

The design solution is a linear receiver for working with high pressures of Bitzer brand F562K, volume 56L.

Layout plans of air conditioners, piping, connection diagrams are presented in the graphic part on the working drawings Sheet 16 - 18.

Specification of equipment and materials is given in

Annex No. 17 to the Explanatory Note.

6.3. System management and automation.

The precision air conditioning system is controlled by the C7000 Advanced controller.

The controller is installed on two air conditioners (the first K1 and the final K9 in the circuit). Controller controls compressor speed by acting on EC-

drive. In addition, it receives signals from pressure sensors and temperature sensors with a negative temperature coefficient in order to monitor whether the compressor is operating within the allowable range, and to control the electronic expansion valve depending on

overheating temperatures. According to the incoming signal from the microprocessor board, it modulates the speed of the compressor to adjust the cooling capacity depending on the actual

heat load.

The controller is also provided with an expansion board to provide

systems with additional discrete inputs-outputs.

The high pressure switches initiate the compressor shutdown as soon as the pressure inside the coolant circuit exceeds 37.8 bar. As soon as the pressure drops below 28.8 bar again, the alarm from the high pressure switch is switched off.

Two pressure sensors are installed on the suction and pressure side of the compressor to monitor the performance of the compressor.

Three temperature sensors with a positive temperature coefficient and three temperature sensors with a negative temperature coefficient are connected to the analog inputs of the controller to measure the following parameters:

- 3 recirculating air temperature sensors, which are located behind the air inlet - upper, middle and lower parts. They are negative temperature sensors and are connected to the C7000 controller.

- 3 supply air temperature sensors, which are located on the front panel of the air conditioner - upper, middle and lower part. They are positive temperature sensors and are also connected to the C7000 controller.

Two additional sensors with negative temperature coefficient are located on suction and pressure side of compressor and are connected to compressor drive and electronic expansion valve. The sensor on the suction side transmits a signal to the controller board to control the expansion valve. The pressure side sensor is used to monitor compressor performance.

Thus, the room air parameters are controlled by built-in temperature and humidity sensors located inside the air conditioner.

This equipment allows remote monitoring and control of its operation over the LAN, using the WIB board installed in air conditioners.

6.4. Organization of erection and commissioning works

By the beginning of the works on installation of equipment and pipelines, all preparatory works must be performed. The set of works providing installation, adjustment and commissioning of equipment is called installation. The reliable and effective operation of the PCOS depends on it. The installation includes the steps below.

Equipment acceptance.

Its external inspection is carried out, if visible defects and damages received during transportation are found - an act is drawn up with a list of defects and determination of deadlines for their elimination.

Installation of air conditioner and condenser unit.

Capacitors KSV045A22 and CSLA20RH are installed on supporting structures (see construction assignment) and are reliably fixed. All equipment is installed strictly horizontally.

Installation of process pipelines.

Pipelines are mounted from copper pipes (for water supply - from ordinary copper, for refrigerant - from special refrigerated copper with a lower content of impurities of other metals), pipe attachments are installed through 1... 2 m, connector connections are not allowed, pipe docking is carried out by brazing. Pipelines for condensate and waste water drain from steam humidifiers - metal plastic pipe. Soldering of copper pipe with brass parts of receiver and valves of winter starting unit is performed by soldering with silver content of 42%.

Test of equipment and external pipelines for density and strength.

It is performed strictly in accordance with SNiP 3.05.0584 p.5.

Evacuation of the refrigerant system.

It is performed by vacuum pump up to residual pressure of 20 mmHg.

Filling with refrigerant.

It is carried out when the machine is operating through the gas line with liquid coolant, according to the manufacturer's instructions.

Adjustment and setting to operating mode.

These works are carried out as part of individual tests at full load of process equipment. In the process, equipment functionality is established, sensor setpoints are determined and automation devices are checked and adjusted.

Acceptance of works.

It is carried out after complex testing of equipment under load under condition of emergency-free operation of PCMS and maintenance of specified parameters of cooled air during testing. In the process of acceptance, certificates are signed and technical documentation is handed over to the Customer.

List of compiled acts

- act of construction readiness of premises for installation;

-act for hidden electrical works;

-act for hidden works on piping installation;

-act for hidden works on piping installation;

-act of pressure test for tightness;

-act of hydrostatic leak test;

-act of individual equipment testing;

-act on results of integrated testing of climatic installations;

- commissioning certificate;

-act of works delivery and acceptance;

-act of training.

Equipment operation

All equipment of the air conditioning system operates automatically under condition of uninterrupted power supply.

It is advisable to carry out maintenance of the equipment in accordance with the instructions of the manufacturing plant.

6.5. Environmental protection and working substance characteristics.

This air conditioning system uses a working substance, Freon R410a.

Description R410a.

Freon R410a is a double azeotropic mixture of hydrofluorocarbons R32 and R125 at equal weight fractions of components (50 and 50%). Global warming potential HGWP = 0.45. Ozone depletion potential ODP = 0. Serves Freon R410a as a refrigerant alternative to R22 and is designed to fill new high pressure air conditioning systems. Freon R410a has a cooling capacity of about 50% higher than R22 (at a condensation temperature of 54 ° C) and a cycle operating pressure of 35... 45% higher than R22.

When installing equipment on the R410a Freon, follow the following guidelines:

- prevent ingress of contaminants into the hydraulic circuit;

- during soldering of pipelines they must be filled with inert or low-reactivity gas, for example, nitrogen with low moisture content;

- perform vacuuming especially carefully;

- coolant refilling shall be performed exclusively in liquid phase.

The safety regulations prohibit smoking or working with an open flame if there are leaks of freon or its concentration in the air above the established standards. Welding and soldering works on devices and pipelines are performed only after removal of coolant from them and with observance of fire protection measures.

The operating organization must periodically check the tightness of the system. The chladone valves are installed so that during repair work it was possible to evacuate the coolant to a linear receiver, which is calculated taking into account the length of the route. The main condition that allows to limit as much as possible the harmful impact on the environment of installation and repair work, as well as the operation of PCMS, is strict compliance with the necessary technological regimes, rules and requirements of safety and labor protection.

The technical solutions adopted in the working drawings comply with the requirements of environmental, sanitary, fire and other standards applicable in the territory of the Russian Federation and ensure safe operation of the facility for life and health of people, subject to the measures provided for in the working drawings.

The spent freon shall be disposed of in accordance with the manufacturer's instructions, qualified by personnel according to these works.

Section 7

Technical and economic part.

7.1. Feasibility comparison of options.

Within the framework of this section, a feasibility study of the design decision on the use of a ventilation plant equipped with a heat recovery system is carried out.

The justification is made using the example of comparison of possible versions of devices and joint operation of plenum unit P1 and exhaust unit B1.

7.2. Brief description of the system.

The project provides for the use of Carrier equipment. The plenum unit P1, in order to ensure the possibility of heat utilization, works together with the exhaust unit B1 and organizes inflow in regulated volumes in the office part of the building. Heat recovery is provided using a system with a rotary recuperator. Partial heat recovery of exhaust air, final overheating of the plenum in winter time is carried out in air heaters from the own boiler room. In summer, pre-cooling of supply air in the rotary recuperator, as well as its cooling in the air cooler of the supply system P1 in the warm period of the year, is provided by the air cooling refrigerator. The required set of functions of P1 installation in the cold period of the year includes:

- filtration of supply air, heating of supply air in recuperator of heat recovery system,

- heating of supply air in the heat supply system calorifer from the own boiler house.

In the warm season:

- supply air filtration

- cooling in recuperator

- post-cooling in the air cooler from the refrigerating machine.

The necessary set of functions of B1 installation in the cold period of the year includes ensuring the utilization of exhaust heat by the designed system, for which the design provides for a rotary recuperator; in a warm period - ensuring the operation of the air conditioning system of the already specified refrigerating machine.

Air capacity of designed systems: 9720 cubic meters/hour, average heat consumption for the heating period excluding recovery: 121.3 kW, maximum heat power of the recuperator: 108.7 kW.

The feasibility study is carried out to evaluate the following engineering solutions:

• application of heat recovery in the design of ventilation plants (cost-effectiveness assessment with determination of the time of return on capital costs for equipment);

7.3. Determination of capital costs for purchase and installation of equipment.

In this section, it should be noted that the engineering solution for optimal power and capacity selection of ventilation plants provides significant cost savings. It is known that when selecting plenum and exhaust plants in most cases, one should strive to increase them in capacity (air capacity), if this is possible. This is due to the fact that low-capacity equipment with an air capacity of up to 40005,000 cubic meters/hour, for most manufacturers, belongs to compact class equipment and, accordingly, moves to another price group.

Thus, the cost of a standard plenum unit intended for installation in an atmospheric closed vent chamber (on average approximately 14 rubles/( cubic meters/h)) turns out to be 2.21 times lower than the cost of an equivalent installation of a compact class (31 rubles/( cubic meters/h)) .

The only significant limitations of the consolidation of installations by air capacity may be the architectural features of the building or the peculiarities of technological processes in it, when it is not allowed to combine a number of rooms with a single ventilation system.

Examples of such restrictions are presented in the framework of the project under development. For example, the administrative part of the building, and the operating rooms No. 1 and No. 2 are serviced by various independent ventilation systems.

Nevertheless, all ventilation plants have significant productivity, and the architectural features of the building allow in all cases the use of standard plenum plants designed to be installed in air-proof ventilation chambers. This enables you to purchase units from the most affordable price group.

It is important to note that application of recuperator for pre-heating of supply air in ventilation plants requires additional capital costs.

The refrigeration machine for operation of the air conditioning system shall be provided by the design in any case.

Capital costs for equipment purchase and installation are determined on the basis of the data of equipment suppliers and SNiP IV582 Estimated norms and rules. Collection 20..

1. Plenum unit and exhaust units without heat recovery system and with basic set of sections:

- intake valve,

- filter,

- calorifer,

- fan unit.

Cost - 26000EU • 43.3 = 1125800 rub.

Automation - 433000 rubles.

Total 1558800 rubles.

The installation cost is 779400 rubles.

Total: 2338200 rubles.

2. Plenum and exhaust units with basic set of sections with heat recovery:

- intake valve,

- filter,

- heating heater and cooling heater,

- fan unit (supply and exhaust),

- rotary recuperator

Cost - 27400 EU (27400 * 43.3 = 1186420 ruble).

System automation = 433000 rubles.

In total in the amount of 1,619,420 rubles.

Installation cost - 809710 rubles.

Total: 2429130 rubles.

Thus, the capital costs for the purchase and installation of heat recovery equipment will be:

- for the system variant without heat recovery:

K1 = 0 rub.

- for a variant equipped with a heat recovery system:

K2 = 123405 rub.

7.4. Determination of annual operating costs.

A. The power consumption costs of the ventilation unit shall be determined by the following formula:

Eel = Zp • Nrab • Nust • Sal;

Where:

Zp = 9 - number of hours of ventilation equipment operation per day, hour;

Nrab = 312 - number of days per year of plant operation, days;

Nust - equipment installation power, 4.5 kW/h;

Sal is the cost of electricity.

For legal entities for 2013 in Chimkent Sal = 11.33 tenge/kWh ≈ 2.36 rubles/kWh;

Thus:

Power consumption costs for a plant not equipped with a heat recovery system:

Eel1 = 9 • 312 • • 4.5 • 2.36 = 29821 RUB/year

Power consumption costs of a plant equipped with a heat recovery system:

Eel2 = 9 • 312 • • 5.5 • 0.8 = 36448 RUB/year

B. Heating costs for ventilation shall be determined by the following formula:

Event = Zp • ZOP • Qust • CT • (1ne);

Where:

CT is the cost of a unit of thermal energy.

For legal entities in Chimkent for 2013 is 6374 tenge/Gkal ≈ 1330 rubles/Gkal;

Qust - average heat consumption of equipment during the heating period, kW,

ZOP - the duration of the heating period in a year, days.

ne - efficiency factor of heat recovery system, assumed equal to 0.45

Then:

Heat consumption from urban networks for ventilation (in case of heating of ventilation plants not equipped with a recycling system).

Event1 = 9 • 160 • • 121.3 • 1330 • • 0,086/100 = 199790 RUB/year

Heating costs for ventilation (in case of heating of ventilation plants equipped with heat recovery system):

Event2 = 9 • 160 • 121.3 • • 1330 • (10.45) • 0,086/100 = 109884 RUB/year

7.5. Determination of annual depreciation charges.

Determined by the following formula:

Eam = 1.5 • K/Tam;

where K - capital expenditures for heat-recovery equipment, RUB;

There - the estimated service life of the equipment, years. In our case, a period of 15 years has been adopted.

Note: this formula takes into account the cost of full reimbursement of the cost, as well as major and current repairs of the equipment.

Thus, for a variant not equipped with a heat recovery system, annual depreciation charges will be:

Eam1 = (1.5 • 0 )/15 = 0 RUB/year;

For a variant equipped with a heat recovery system:

Eam2 = (1.5 * 123405 )/15 = 12340 RUB/year;

Total annual operating costs will be:

E = Eel + Et + Eam, rub/year.

1 variant (without heat recovery):

E1 = 29821 + 199790 = 229611 rub/year

2 variant (with heat recovery):

E2 = 36448 + 109884 + 12340 = 158672 rub/year

7.6. Determine the total costs charged.

The total discounted (quoted) costs - WBS - for each variant are determined by the following formula:

SDZ = K • (1 + p/100) T + E • ((1 + p/100) T-1) • (100/p), RUB;

where K - capital expenditures, in this case K1, K2, RUB;

p - discount rate,%. We take p = 18%.

To assess the effectiveness of additional capital investments and determine their payback period, it is necessary to build schedules of the dependence of SDZ1 and SDZ2 on T and find their intersection point.

Output:

1. According to the data obtained, the use of plenum air heating, since the operating costs for electricity in this case are significantly lower compared to the costs for thermal energy in centralized heating of plenum plants (199790 and 109884 rubles/year, respectively), is not only permissible, but also preferable;

2. The estimated payback period of Trasch for additional capital investments in the heat recovery device in our case was slightly less than 4 years (see chart), which is significantly less than Tam = 15 years. Therefore, starting with T = Trach, we make a net profit due to energy saving.

Therefore, heat recovery is cost effective.

Section 8

Automation.

8.1. Description of the automation object.

The automation and control project of heating, ventilation and air conditioning systems is carried out in accordance with the requirements of SNiP 41012003 "Heating, ventilation and air conditioning" (SNiP RK 4.02422006) and taking into account the recommendations of the publication "Automation and automation of heat and gas supply and ventilation systems," ed. V.N. Boslovsk.

Design Object Data:

The purpose of the building is the administrative building of the regional branch of the telecommunications operator,

Storey - three floors, including the operating basement,

Construction district - Chimkent, Kazakhstan,

The project provides for automation and control of heating processes, air treatment in plenum chambers equipped with a heat recovery system for exhaust air.

8.2. Providing automation and control of the facility.

Automation of systems is provided in the following volume:

In the thermal points of the complex, controllers have been designed to maintain the necessary temperature and pressure parameters in the supply and return pipelines of heating and cooling systems.

Plenum ventilation systems are equipped with control, interlocking, regulation and control facilities.

These tools provide:

- control of ventilation system motors,

- control of external, recirculation and discharge air damper drives,

- control of supply air temperature in accordance with the specified values.

The project provides for disconnection of power supply to ventilation units in case of fire.

Ventilation systems in the designed building must not only meet sanitary and hygienic requirements and safety requirements, but also be perfect in terms of comfort and quality from the point of view of aesthetic perception. The appearance of noise, vibration, blast should be completely excluded. High demands are placed on saving thermal and electrical energy.

The physical processes of energy absorption, conversion and transfer in enclosing structures and premises of the building, as well as in heat and mass exchange devices of the air conditioning system, flow over time and are thus dynamic processes.

As a result of these processes under the influence of external and internal disturbances, a microclimate of building premises is formed as a set of interconnected parameters. Preset values of microclimate parameters in room can be provided by means of control actions.

External disturbances include changes in external climate parameters, air speed, solar radiation intensity.

Internal disturbance effects include varying inflows of heat, moisture, harmful gases from people, technological equipment, heat input from indoor lighting.

Maintaining microclimate parameters at a given level makes it necessary to control microclimate formation processes under constantly changing external and internal influences.

The task of SLE control is to actively intervene in the course of the process of air processing by means of control channels, to generate tasks for values ​ ​ of controlled states, to introduce control actions on the implementation of a set of technological processes, i.e. to implement a certain technological mode in order to reduce energy consumption by the air conditioning system.

The building microclimate control system is a set of technical means that receive and process information on the states of the air processing process, and maintain the specified values ​ ​ of the microclimate parameters in the serviced rooms. This takes into account the functioning of the system in conditions of continuous exposure to disturbances, ensures the rational flow of a particular process of air treatment, as well as their sequence.

Currently, the most common in air conditioning systems is the automatic regulation of microclimate parameters with machine controls, which is often enough with comfortable air conditioning in civil and residential buildings. The main functions of the automatic control system along with accurate maintenance of the specified values ​ ​ of the microclimate parameters (stabilization or program automatic control) are:

- Monitoring of the state of individual elements and the whole system,

- Equipment overload protection,

- Locking of individual components to ensure safe operation,

- Reduced consumption of electricity, fuel and thermal energy.

Special attention shall be paid to increase reliability and service life of equipment, pipelines and valves. One of the main ways to achieve this is the rational use of automation tools in the necessary and sufficient volumes, thereby creating an additional reserve of reliability of the systems in accordance with the requirements of the customer.

In some cases, the competent use of automation means can avoid undesirable phenomena. For example, hydraulic shocks, deposits of scale and salts in heating system devices, reduction of destructive effect on steel pipes of oxygen involved by heat carrier, etc.

The design of the fire smoke removal system also requires reliable automation tools. The specifics of this system is that it is not used for years, with the exception of control scheduled launches (in accordance with fire regulations) during inspections by the fire inspection. As a result, the system may, if necessary, be unable to perform its tasks for a variety of reasons. Among the latter may be: disassembly of systems, unauthorized design changes, malfunction of units and parts of the system, operational errors.

Important from the point of view of engineering systems design is the requirement of the customer to take into account the possibility of redeveloping and repurposing the premises of the building, which is quite possible under today's economic conditions (so some premises in the building can be transferred to other owners, which will entail a revision of the procedure for using engineering systems). Changing the conditions in the premises of the building will entail the application of system control, these functions will be assigned to automation and control systems.

Important reasons for the introduction of advanced, reliable and easily controlled automation tools are energy saving conditions, high requirements of construction customers, as well as the opportunities that are currently open to the developer due to the presence of a large range of both Western and domestic modern equipment.

8.3. Design and technological solutions adopted.

In the systems, it is planned to use standard equipment according to the catalogs of manufacturers. Automation tools for HVAC and Heat and cold supply systems are supplied by the manufacturers of the main equipment.

So, in order to meet the requirements of SNiP 41012003 and recommendations, the heating system provides for the regulation of heat removal of heating devices using Danfos automatic thermostatic valves. When the heat requirement of the room changes, the valve automatically changes the flow rate of the coolant passing through the heating device.

Electronic controllers of the type ECL Comfort 300 from Danfos are installed in the thermal point of the building.

ECL series electronic regulators are designed to maintain the coolant temperature in the water heat supply systems in proportion to the outside air temperature and constant temperature in the hot water supply system.

Regulators control motor valves on heating water pipelines depending on temperature sensors readings.

Regulators have thyristor outputs for control of control valve drive and relay outputs for control of boiler pump or burner device. Up to six temperature sensors, remote monitoring and control panels, additional relay and communication modules can be connected to the regulator. ECL Comfort 300 controllers are designed for wall mounting, for installation in a control panel cutout or on a DINrack. Regulators have built-in

RS232 Media Module with front panel connector.

The ECL300 has a built-in timer for changing time control modes and a large information display. They are switched from one application to another using control information cards inserted into the regulator. Each map ensures the functioning of the regulator but for a specific heat supply scheme.

The selection of the map and specific settings of the regulator is determined by the requirements of the heat supply scheme.

Some examples of applications for the ELC 300 regulator are:

The display displays information about the status of the heating and heating system of the funcoils. Programming of time and system parameters is shown on one of the displays, which can be selected as operating. The display is also used to set adjustment parameters.

The present design provides a control card of the P30 type, which is rusticated, the application of which is the control of valves and pumps in a heating system with plate water heaters.

In order to save electricity and ensure better automatic system control conditions, the installation of circulation pumps from WILO is provided in the heat station.

Also, as an object of automation and control, within the framework of this project, a complex of devices is considered, which includes a plenum unit P1, an exhaust unit B1, and a heat recovery system for exhaust air.

The project provides for the use of widely represented equipment on the Russian market for automation systems of Carrier (manufactured in the USA, France). The plenum unit P1, in order to ensure the possibility of heat utilization, works together with the exhaust unit B1 and organizes the inflow of office premises into the room.

System of year-round use and equipment:

- air intake valve,

- pocket filter,

- heat recovery device,

- air heater,

- air cooler,

- fan,

- silencer,

- control and automation cabinet.

Heat recovery is provided using a heat recuperator.

The required set of functions of P1 installation in the cold period of the year includes:

- cleaning of supply air in filters,

- heating of the supply air in the calorifer of the heat recovery system,

- additional heating of supply air in the air heater,

- supply by means of fan section and system of air ducts to serviced rooms.

In the warm season:

- cleaning of supply air in filters,

- air cooling in air cooler.

- supply by means of fan section and system of air ducts to serviced rooms.

The required set of functions of B1 installation in the cold period of the year includes:

- provision of exhaust air heat utilization by the designed system.

The air intake device of the plant is equipped with an insulated valve of the HVC type, equipped with an electric drive (BELIMO NM 230AS type) for automatic opening - closing.

To monitor the dust content of the filter and fan operation, a differential pressure sensor (differential pressure gauge on the unit housing) is installed.

The freezing protection pump is activated when the two-way valve operates, which prevents defrosting of the system.

The fan is equipped with an on/off drive.

Temperature sensors: control of supply air temperature, protection against freezing of the heat exchanger by water and by air.

The alarm means are the output of the intake valve open-close indicator, fan operation indicator, filter operation indicator to the control panel.

With the help of automation, the supply and exhaust systems are disconnected in case of fire with simultaneous automatic closing of air intake valves.

Main sections.

An air valve is required to control the amount of air (external and recirculation) entering the central air conditioner. In all cases, for opening the valve when the fan is turned on and closing when the electric drive of the receiving valve is switched off with the fan motor. When the fan motor is switched on, the valve opens, when the fan motor is switched off, it closes.

Control automation also involves locking valves in systems with an exhaust fan, when the valve is turned off in the exhaust air.

Filter

Air cleaning from dust is two-stage. Filters are placed in those parts of the air conditioner through which all treated air passes so as to protect as many air conditioner sections as possible from dust.

In pocket filters, the area of the filter material through which the cleaned air passes is several times larger than the area of the front section of the conditioner, which allows reducing the aerodynamic resistance of the filter, increasing the filter operation time between regeneration, and increasing the filter service life. All filters can be operated at temperatures up to 60 ° C.

Pocket filter is installed on single frame and fixed by means of latches. Replacement of the pocket filter, which is installed on the frame from the side, for which it is necessary to provide a space in front of the filter not less than the width of the plenum unit.

For ease of operation, the air filter is equipped with a differential pressure gauge measuring the pressure drop before and after the filter. The differential pressure gauge is equipped with a signal lamp, which turns on if the aerodynamic resistance of the filter exceeds the preset one.

The second filter of finer cleaning is located behind the first one along the air flow and in it more fine air cleaning is carried out.

Air heater

Water air heaters have heating elements - a drawn copper tube, on which aluminum plates are fitted, which create external finning of the tubes in order to increase the surface of heat exchange from the air side and the total heat transfer intensity. For the heat transfer process, it is very important to ensure good contact between the pipe and the fins, which is achieved by mechanical deformation of the pipe in factory conditions during the manufacture of heat exchangers.

Emergency-free operation of the air heater is served by freezing protection, which includes a circulation pump, a valve with an electric drive on the return pipeline of the coolant, as well as a check valve on the bridge.

The pump is switched off in operating mode. If in the return pipeline the temperature sensors record a decrease in the coolant temperature below the specified value (810 ° C) or the air flow temperature sensor downstream the air heater below the specified value (610 ° C), the supply and exhaust fans are switched off, the air intake valve is closed and the valve for coolant passage is opened. At the same time, the signal "Freezing danger" is transmitted to the automation board or to the control panel.

Air cooler

The cooling section is a water heat exchanger made of copper tubes with aluminum fins. The refrigerant can be: chilled water, a mixture of water and glycol, freon. In this project, the refrigerant is water. Finning of tubes with plate fins provides high heat transfer at low aerodynamic resistance of heat exchanger.

Automation of heat exchangers is connected with regulation of cooling capacity of air cooler. Since it works only in the warm period of the year, the automation circuit is activated only when the selector switch in the zimaleto control panel is in the "summer" position.

A three-way valve is installed on the return coolant pipeline, which allows to reduce the coolant flow rate through the air cooler, and thus the water flow rate along the cooling machine circuit remains constant.

Fan

Fan section is designed for air transportation and its supply to serviced rooms. One-way and two-way low and medium pressure suction radial fans are used. Depending on the required capacity and head, fans with rotor blades bent forward or with blades bent back are used, which provides easy control of the network parameters. The fans are highly efficient and allow you to adjust the performance by changing the number of revolutions.

Automatic means provide protection that stops the fan from operating when the intake valves are closed, since otherwise the pressure in the plenum unit may be higher than the maximum permissible.

For this purpose, a pressure gauge with an electric contactor is installed and special fan power switches are provided.

8.4. Object Management Functional Diagram

Main functions of the designed automation and control system: - room temperature control year-round;

- setting the temperature from the room;

- heat recovery of exhaust air;

- closing of air valves during "waiting" periods;

- heating of supply air;

- cooling of supply air;

- maintenance of minimum temperature during "waiting" periods.

The system operates as follows.

The actuator (FAD) of the supply air valve has two modes: "open" and "closed." If there is a need to block the air supply (e.g. by fire alarm or by stopping the system fans), the valve is set to closed. The operation of the filter is monitored by a pressure sensor (PF), which, if an unacceptably high differential pressure is reached for a given type of filter, will statically show the difference value, which will give grounds for the employees of the operating services to replace or clean the filter. Control of temperature of incoming air is made for ensuring work of a system of heatutilization by thermal sensors (T). The operation of the supply and exhaust fans is also monitored using differential pressure sensors.

The possibility of emergency disconnection of fans from the control panel of the indoor ventilation chamber is provided. On the supply fan, this is done using a manual toggle switch, actuation of the disconnecting device. On the exhaust fan - using a manual toggle switch and actuation of the disconnecting device.

Maintenance of the specified temperature in the serviced rooms is provided by the temperature sensor installed in the room.

Setting of the required temperature in the room and its regulation in real time is carried out by manual regulator using manual switch. The exhaust air valve actuator (EAD) has two modes: "open" and "closed." If there is a need to block the air inflow (for example,

by fire alarm signal or in case of system fans shutdown), the valve is set to "closed" position.

Heat utilization system operation is ensured by means of secondary circuit control elements. The actuator (V1) controls the coolant supply with a three-way valve. The switch operates discretely and has two states: on/off. In the ON position, the circulation pump of the system is operated.

If it is necessary to disconnect the ventilation system (for example, by a fire alarm), the fans are automatically disconnected using actuators (FAD and EAD), which bring the valves to the "closed" position.

The system assumes the use of controllers capable of proportional-integral regulation. In order to reduce the cost of the system, it was decided to maximize the unification of automation and control equipment with the standard versions offered by the company to the supplier of ventilation equipment.

Two controllers are supposed to be used at once.

Controller # 1 comes complete with a typical 39HQ vent unit automation diagram from the Carrier catalog. This controller has a digital display, allows the system to operate in master-slave mode, has adjustable settings/

Controller No. 2 (NTC) communicates between the system components, controls the operation of the fan unit motors, controls air valves at the air inlet and outlet and lighting. Thus, among the advantages of the proposed device is the possibility of modifying the system operation algorithm already at the commissioning stage, and not at the design stage, which significantly simplifies the debugging of systems on site. In addition, the controllers combine the controller and the arithmetic device, which makes it possible at the design stage to completely abandon any other (for example, relay) control schemes for the operation of a complex object, such as the system proposed in this project.

Thus, the selected device meets all the requirements for it in the framework of this project.

Section 9

Organization of works.

9.1. Procedure for organization of works.

The Work Execution Project (WP) is the main guide for the organization and execution of erection work at the site. The WDP helps to plan all preparatory work, including ordering of pipelines, ducts and requests for heating and ventilation equipment and materials, to determine the place of storage. The WDP contributes to uninterrupted installation work, reducing the cost and duration of work, improving the quality of installation and reducing injuries.

The complete work design includes the following sections:

- situational plot plan with assignment of storage places of pipelines, air ducts and equipment;

- Schematic layout of the facility with location of ventilation equipment and heating system inlet;

- list of heating and ventilation equipment supplied by the customer;

- characteristics of air ducts for ventilation systems and list of installation drawings on them;

- specification of pipelines for heating systems and list of installation drawings on them

- Work and safety instructions; Production Costing and Labor Cost and Payroll Summary.

The complete PPM includes:

- schedule of ventilation and heating billets and equipment arrival to the facility,

- work execution schedule (network),

- list of necessary mechanisms, tools and means of small mechanization,

- Material and Auxiliary Bill of Materials,

- schedule of demand for workers,

- technical and economic indicators,

- explanatory note.

Three sections of the PWP shall be pre-agreed with the general contractor:

- schematic plan of the facility with application of equipment storage places,

- work execution schedule (network),

- Section of the Instructions for Works, which provides recommendations for installation and application of winch and block fasteners to construction structures and installation of air duct and equipment fasteners.

In the schedule (network) of work execution, the dates of preparation of the object or individual rooms for installation, the dates of completion of construction work in the ventilation chambers and the heat station, the dates of supply of electricity to the ventilation equipment and hot water to the calorifers should be specified.

A schedule for the supply of ventilation and heating equipment to the facility should be previously agreed with the customer's organization. If these conditions are met, the PPM becomes a valid document determining the sequence, duration and quality of installation ventilation and heating works.

For objects with a small volume of ventilation and heating works and major repairs, the abbreviated PPM, which includes:

- brief instructions for erection and safety,

- installation work schedule,

- schedule of receipt of ventilation and heating billets, materials and equipment to the facility,

- brief explanatory note.

The Work Execution Design shall be based on working drawings, estimates, construction guidelines and Work Execution Schedule agreed with the General Contractor.

With modern industrial construction methods, the production of assembly ventilation works requires careful preparation. This work in the installation departments is carried out by special production preparation areas (SCP), which, as a rule, are part of the production and technical department (STP). The ITP is directly subordinate to the Chief Erection Engineer. Technical documentation for the performance of works: design, estimate, documents on the readiness of work, work orders passes through the TRP.

The production preparation area is responsible for:

a) study of design documentation;

b) identification of possibility of complete or partial replacement of rectangular air ducts with round air ducts;

c) identification of the possibility of replacing atypical ventilation parts with typical mass-produced procurement enterprises;

d) coordination of the proposed project changes with the relevant project organization;

e) development of installation drawings or sketches for measurements in kind;

f) preparation of work execution projects;

g) making and issuing orders for the manufacture of air ducts of other parts;

h) coordination of work schedules with procurement enterprises and monitoring of order execution dates;

and) compilation of consolidated lists of assembly blanks, products and equipment required for installation works

for construction facilities;

k) drawing up limit maps for basic materials, products and equipment for construction facilities;

l) check of readiness of construction facilities for installation of ventilation devices;

The work execution project is a guide to the organization and execution of installation works and helps to reduce the cost of work, reduce their duration and improve the quality of construction.

9.2. Acceptance of the object for installation works

Prior to the start of installation work on the site or on its part (capture) between representatives of the installation organization and the general contractor, a list of certain types of construction work related to the installation of ventilation and heating systems and their deadlines must be agreed.

Such works include:

1. Installation of foundations, platforms and other supporting structures for ventilation equipment;

2. Installation of walls and partitions in ventilation chambers, as well as ceilings, if the PPM does not provide for supply of ventilation equipment through the top of the chambers;

3. Installation of embedded parts of ventilation chambers and heat station provided for the design for connection of ventilation and heating equipment and along the route of systems for attachment of air ducts and pipelines;

4. Arrangement of horizontal and vertical mounting openings for supply of ventilation, heating equipment, air ducts and pipelines with object storage to the place of installation;

5. Construction of walls and floors in places of air ducts and pipelines laying;

6. Plastering and painting of walls, floors and partitions in places where air ducts are laid and air terminals are installed;

7. Punching of holes in places where air ducts and pipelines pass through walls, floors, partitions, if they are not left during building erection;

8. Installation of attachments for large air ducts and sites for cyclones, scrubbers, filters, etc.;

9. Glazing of windows and lights;

10. Cleaning of places of ventilation and heating works from construction debris.

Especially carefully prepare the rooms of ventilation chambers, where all construction works (except for clean floors and final painting) must be carried out and design lifting devices for operation and repair of ventilation equipment should be installed. For the passage of air ducts through building structures, the holes shall be 150 mm larger than the diameter of the round duct and the dimensions of the sides of the rectangular duct.

9.3. Installation Engineering

Assembly design is carried out on the basis of working drawings of ventilating devices of the OV brand and the corresponding architectural construction plans of the ARE brand. In some cases, process drawings of steel structures of KM grade of reinforced concrete structures of KZ grade are also required. Installation drawings included in the installation design have such a degree of detail of assemblies that it is possible to manufacture these assemblies in factory conditions with an accuracy close to the accuracy of manufacturing machine parts.

In the design of assemblies, usually normalized shaped duct parts and straight sections of standard length are used. Air duct fasteners and connecting elements of the network are provided mainly from among those that are mass-produced by procurement enterprises. The installation drawings comply with the current installation provisions, i.e. the requirements for the placement of air ducts and ventilation parts in relation to building and other structures, as well as among themselves, which do not provide convenient installation and safe operation of ventilation devices.

Air ducts of ventilation systems are manufactured at the plants of ventilation blanks and workshops only according to installation drawings or sketches. Installation drawings shall be executed either by the personnel of the production preparation department of the installation control, or by specialized departments of the installation design of design institutes based on the working drawings of ventilation systems. Installation drawings contain:

a) The axonometric diagram of each ventilation system, made without scale, in one line, indicating the dimensions of the cross sections of the ducts, the number of each part, the elevations and references of the ducts to the axes and surface of building structures;

b) Picking list with list of all parts, their dimensions, characteristics, quantity and reference to GOST;

c) Sketches of abnormal shaped parts of air ducts;

d) Scope of work and specification of materials and standard components, including type and number of units and fixtures.

Thus, in addition to the ventilation network diagram, the installation drawing shows the picking list of parts, the scope of work, and the specification of the main materials. The pick list indicates the number, dimensions, and surface area of duct parts by their sequence numbers. The dimensions and quantity of all connecting and fastening parts, as well as air distribution, control and auxiliary devices included in this ventilation network and to be manufactured by the procurement enterprise are also included in the pick list. The non-normalized shaped parts of the ducts are sketched with the required dimensions. Each sketch has a reference to a corresponding sequence number.

9.4. Installation of ventilation equipment.

Installation of fans shall be performed as per thermal flow sheets (TTK). According to the degree of installation complexity, fans can be divided into three groups:

a) Radial fans No. 2.5 and 3.2 with an electric motor on the same network or axial fans No. 4; 5; 6; 3 and 8. The overall dimensions of these fans are not large, and the mass does not exceed 50 kg.; transportation to the installation site is usually not difficult;

b) Radial fans up to No. 12.5, axial fans above No. 8 and all roof fans weighing up to 1400 kg, supplied in assembled form with an electric motor, frame, gear; such fans are called fan units. The fan of this group is usually mounted without disassembling the unit. To transport them and lift them to the installation site, lifting mechanisms and mounting openings are required;

c) Radial fans No. 16 and above. The mass of these aggregates reaches several tons. They are supplied by separate enlarged units: a fan casing of several parts, a drive unit (a frame with an electric motor and V-belt transmission), a shaft unit with an impeller, vibration isolators. For installation of such fans, enlarged units are supplied to the installation site, and the unit is assembled on the foundation.

Fan locations can be located in different locations in buildings. Fans of plenum systems and air conditioning systems are usually installed in the basement.

Fans of powerful ventilation systems are mounted at the floor level so that vibration from their design is not transmitted to the building structures.

They are mounted as in special rooms - ventilation chambers. With this installation of fans, the working area of ​ ​ the floor of the workshop is freed.

Exhaust system fans are usually mounted on technical floors or on the roof of buildings.

Before starting the installation of fans, a number of preparatory works should be carried out: accept the premises of ventilation chambers, platforms, foundations and other supporting structures for installation; prepare and install lifting devices and mechanisms, check dimensions of all mounting openings and passages, deliver ventilation units to the installation area.

Reception of rooms of ventilation chambers is executed by act. It is especially necessary to check the compliance of design data of actual sizes of foundations, embedded parts.

Fasteners of lifting mechanisms must comply with the instructions of the PPM, and in case of deviations from the PPM, they must be agreed with the general contractor. To start installation of the fan, check the compliance of the equipment with the design data and the completeness of the delivery according to the factory picking list. At the warehouse, check the type of fan, its direction of rotation, number, design, type of electric motor, its power, purity of rotation, diameters of pulleys. If one or more parameters do not match, installation can be allowed only after approvals of changes with the design organization.

Installation of fans and central air conditioner (CC) is performed in the following sequence:

1. Deliver the fan and the Central Committee to the installation area by means of vehicles: vehicles, forklifts, trailers, etc.;

2. Fan and Central Committee are slung;

3. Raise (lower) the fan and the Central Committee to the design elevation and set to the design position;

4. Before connecting the air ducts, the balance of the fan - impeller with the shaft, the tension of the V-belt belts, fastening, fencing is checked;

5. Bearings of impeller shaft and electric motor are reviewed and lubricant is checked;

6. Electric resistance of motor winding insulation is checked.

power supply is connected and fan operation is checked, as well as correctness of impeller rotation direction.

Radial fans are usually mounted on spring vibration isolators. DO vibration isolators do not need to be attached to the floor. When installing fans on steel structures or foundations, bolt them through holes in the bottom plate. Elements of steel structure and embedded parts, to which vibration isolators are attached, must coincide in plan with the corresponding elements of the fan frame in order to be able to adjust the position of vibration isolators.

if the ventilation unit units do not correspond to the design data and the center of gravity of the unit is shifted from the design position, then the location of the vibration isolators is determined experimentally. fan is installed on vibration isolators and, moving the vibration isolators along the frame, provides their uniform loading and horizontal position of the frame. When adjusting, the more compressed vibration isolators should be moved away from the intended center of gravity of the unit. Noting the places of final installation of vibration isolators, holes for their attachment are drilled in the unit frame.

The location of the air duct fasteners shall be determined in accordance with SNiP. Fixtures of horizontal metal non-insulated air ducts (clamps, suspensions, supports, etc.) are installed at a distance of not more than 4 m from another at diameters of air duct of round section or dimensions of larger side of air duct of rectangular section less than 400 mm and more. Attachment of vertical metal air ducts is located at a distance of not more than 4 m from each other. Do not attach braces and suspensions directly to the flanges of air ducts. The distance between suspensions or brackets of vinyl-plastic ducts of any sections is accepted for horizontal sections not more than 2.5 m, for vertical ones - 3 m.

When installing air ducts, observe the following basic requirements of SNiP:

a) air ducts shall be securely attached to building structures; air ducts shall not be supported by ventilation equipment;

b) transverse and detachable connections of air ducts should be located outside walls, partitions and floors;

c) vertical air ducts shall not deviate from the vertical by more than 2 mm by 1 m of height;

d) air ducts intended for transportation of humidified air in the lower part shall not have longitudinal joints;

e) dilution sections of air ducts, where condensate can fall out of the transported wet air, are mounted with a slope of 0.010.015 towards drainage devices.

The installation of air ducts, as a rule, should be carried out in the ways provided for by the "Typical Process Instructions for the Installation of Industrial Ventilation and Air Conditioning Systems" (TTK series 7.05.01).

Method of installation of air ducts is selected depending on their position (horizontal, vertical), location relative to building structures (inside or outside the building, against the wall, near the columns, in the inter-truss space, in the shaft, on the roof of buildings) and on the nature of the building.

9.5. Define quantities of work and calculate costs.

Source Data:

building - two-storey with basement,

walls - cellular foam concrete, administrative purpose.

Designed 2 plenum systems, 6 exhaust and 2 air conditioning systems, smoke removal system. All systems are mechanical. Air ducts are used in rectangular section made of thin-sheet steel.

Ducts are laid in the space of the set ceiling.

Building V = 13250 m3.

9.6. Installation tool for mechanization of installation works

All manual and mechanized tools used in installation

ventilation systems, can be divided into several groups: measuring, marking and control; for metal cutting and sawing; drilling holes; thread cutting; for assembly and installation operations; for welding and gas cutting of metal.

9.7. Organization of work quality control.

High quality and reliability of buildings and structures should be ensured by construction organizations by implementing a set of technical, economic and organizational measures of effective control at all stages of building products creation.

Quality control of construction and installation works shall be carried out by special services created in the construction organization and equipped with technical means ensuring the necessary reliability and completeness of control.

Production quality control of construction and installation works shall include incoming control of working documentation, structures, products, materials and equipment, operational control of individual construction processes or production operations and acceptance control of construction and installation works.

During incoming control of detailed documentation, its completeness and adequacy of technical information contained in it for the performance of works shall be checked. During the incoming inspection of building structures, products, materials and equipment, it is necessary to inspect their compliance with the requirements of standards or other regulatory documents and working documents, as well as the availability and content of passports, certificates and other accompanying documents.

Operational control should be carried out during construction processes or production operations and ensure timely detection of defects and taking measures to eliminate and prevent them. During operational control, it is necessary to check compliance with the technology of construction and installation processes; compliance of performed works with working drawings, construction codes, rules and standards.

Acceptance control consists in checking and evaluating the quality of installation works. Hidden works are subject to examination with the preparation of acts, each of which is compiled for a completed process.

It is forbidden to perform subsequent works in the absence of acts of inspection of previous hidden works in all cases.