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GB/T 13409-1992 Design parameters and calculation methods for air conditioning and ventilation in ship accommodation spaces

Basic Information

Standard ID: GB/T 13409-1992

Standard Name: Design parameters and calculation methods for air conditioning and ventilation in ship accommodation spaces

Chinese Name: 船舶起居处所空气调节与通风设计参数和计算方法

Standard category:National Standard (GB)

state:in force

Date of Release1992-03-30

Date of Implementation:1993-01-01

standard classification number

Standard ICS number:Shipbuilding and offshore structures>>Shipbuilding and offshore structures in general>>47.020.90 Marine ventilation, air conditioning and heating systems

Standard Classification Number:Ships>>Ship General>>U13 Ocean Transport Ship General

associated standards

Publication information

publishing house:China Standards Press

other information

Release date:1992-03-30

Review date:2004-10-14

Drafting unit:CSSC 708 Institute

Focal point unit:National Technical Committee for Standardization of Marine Vessels

Publishing department:State Bureau of Technical Supervision

competent authority:China State Shipbuilding Corporation

Introduction to standards:

This standard specifies the design parameters and calculation methods for air conditioning and ventilation of accommodation spaces on maritime civil ships. This standard applies to air conditioning and ventilation of accommodation spaces and newsrooms on maritime civil ships. GB/T 13409-1992 Design parameters and calculation methods for air conditioning and ventilation of accommodation spaces on ships GB/T13409-1992 Standard download decompression password: www.bzxz.net

Some standard content:

EDC629.12.05.001-24
National Standard of the People's Republic of China
GB/T 13409—92
Air-conditioning and ventilation design parameters and calculation methods of accommodation spaces on board ships--.Design parameterand method of calculations
Published on March 30, 1992
Implemented on January 1, 1993
Published by the State Administration of Technical Supervision
National Standard of the People's Republic of China
Afr-conditionlng and ventilation design parameters and calculation methods of accommodation spaces on board ships 1. Main interior and applicable standards GB13409-92 This standard specifies the design parameters and calculation methods for air conditioning (abbreviated as air conditioning) and ventilation of civil ships at sea. This standard is applicable to the design and calculation of air conditioning and ventilation of sheltered spaces and sheltered rooms for civil use. 2. Reference standards JT4517 General specifications for transport of cargo in sheltered spaces 3. Terminology |tt||3.1 Living quarters
refers to places used as public places, living quarters, restrooms, dormitories, offices, departments, clinics, cinemas, research centers, public places, non-motorized facilities and similar places.
3-2 Air conditioning areas
refers to places used for living with air humidity, temperature and ventilation, and may also include rooms and sample rooms that are not subject to temperature and humidity conditions.
3.3 The ventilation frequency of the cabin
refers to the ratio of the air delivered to the cabin or other cabins per hour to the average air quality of the cabin. 3.4 The air supply mixing difference
refers to the difference between the air return air density in the cabin and the average air density in the cabin after considering the temperature rise or temperature drop of the supply air. 4 Design factor
4.1--General requirements
The air conditioning system should be calculated and designed in accordance with the requirements of 4.24.6 and should meet the requirements of Meet the provisions of 92.2 series (except where otherwise specified in the design!
When using this standard, the regulations and requirements of each cell design card shall also be met. The actual method can achieve the actual gas safety effect, especially the relative humidity, which can be recommended according to the circumstances of Article 4.2. .2 Summer operating conditions can be well designed and calculated for variable gas conditions and relative humidity, 35 degrees Celsius, 70% cabinet Liu degrees, 27°C + global temperature. 50% cabinet humidity. Note: The above data are applicable to the single wind in the month with no wind and the single wind in the month with rising wind, and can be determined according to the specific conditions of each sailing wind. National Technical Supervision Bureau approved on March 30, 1992, implemented on January 1, 1993, G0/T13409-92, 4.3 Winter working conditions Cabin interior and exterior design air flow and relative humidity Outside: 20°C global temperature: Inside: 22°C global temperature, 50°C relative humidity. Note: The above effect is based on the new ship built in the region of use. If there is a need for wind, the wind can be pushed to the service version of the day to decide, 4.4 Fresh air volume The minimum outside fresh air supplemented by the air conditioning system is as follows. Choose the biggest one among the two methods, and buy fan coil units to meet the requirements in:
Calculate the number of people:
Living room, sex room
Office, public age room
Entertainment room
Passenger ship
According to the total air volume of air conditioning, it is recommended to calculate
28m*/h per person
20-251/1 per person
17--20m/h per person
25m/h per person
For ships in limited navigation areas, not less than 45% of the total air volume of air conditioning, and for ships in unlimited navigation areas, not less than 0% of the total air volume. 4.5 Ventilation frequency of air-conditioned cabins The air intake volume of air-conditioned cabins shall be determined according to the heat that can be obtained and the wind distribution after heat absorption, but shall not be less than the prescribed minimum ventilation frequency per hour to maintain the speed and relatively uniform change of cabin air ventilation. The ventilation system is used to calculate the ventilation changes per hour as follows:
staff room, companion room
office, public bedroom
infirmary, ward
entertainment room
passenger room
4. 6 calculation, upgrade
captain, chief engineer's office
according to the maximum number determined by the design
office of the first mate, second engineer and safety director
restaurant, forestry room, cinema
medical room
entertainment room
5. Heat gain and heat loss are calculated according to the number of seats
and the number of beds added?
According to the design number of passengers
5.1-1 regulations
In summer, the heat loss in the cabin (incoming heat, human body heat, lighting equipment heat) can be calculated according to 5.2~5.6, and the sensible heat and heat loss can be calculated respectively.
In winter, the cabin heat loss is calculated according to 5.7, and other losses are not taken into account, but the cabin personnel, etc. (generally only the human body heat loss is calculated by the low condensation ratio in the first winter) must be calculated, and the sensible heat loss must be calculated. 5.2 Incoming heat
Incoming heat is calculated according to formula (1),
wherein——incoming heat, w,
GB/T13409
1——the sum of incoming heat from the cabin board, cabin barriers, and ship sensible heat loss W:g
glass The sum of the heat input, W:
The sum of the heat input to the shaded deck, the cabin, W; the sum of the heat input to the cabin under normal circumstances, 5-2-1 Heat transfer area
The heat transfer surface is selected according to the distance between the deck and the cabin bulkhead (excluding insulation), 5.2.2 Heat transfer calculation method Www.bzxZ.net
The heat input to the deck, the cabin bulkhead, and the cabin heat transfer is calculated using formula (2). a.
9=A, (—)
Where: 41-H cabin deck, bulkhead, cabin heat input, W, sign times the corresponding insulation transfer system on the heat transfer surface (see 2.3). W/m\K (1)
A,: deduct the sum of the insulation surface and the partition surface 100mm from the outer edge of the glass window (A, >The heat transfer area is shown in 1), m-.—The air temperature outside the cabin is calculated as the air temperature (ground surface 1), ;. The design air temperature inside the cabin is C.
Flash window
Calculation, the whole, the air temperature of the energy side is calculated as 4, m using the daily equivalent air design temperature and H shady side equivalent temperature is almost the same, but, Table 1
(sun exposure, daily resistance average calculation)
Note that the shady side equivalent temperature is close to 38℃,
h. The heat retained is calculated according to formula (3)
-+, A, (t.-r)-C, 41
Where:., the amount of glass window entering the goose. W
Single external equivalent air group test
(external identification air change 35)
Limb glass window and square 1 00mm outer peripheral surface transmission coefficient, W/m*K3
single-layer glass window is 6.6W/xnK
double-layer glass fire 3.5W/m*K
/713409-92
A, -... glass brick window and its 100mm outer comprehensive
circle area (see letter 1) m,
one-year design temperature outside the seat,
... can be designed air temperature inside,
an-sphere high front blocking efficiency rate, research cylinder single-layer end window 350W
single room ordinary glass window has a color old design garden 0W/m2 double-layer free pass glass window has a white. Select the facility 210W/mA, glass window surface type. ".
c The heat transfer of the deck is calculated based on the two surfaces of the 5-ton shading plate. The temperature difference between the inside and outside of the cabin is calculated according to the formula (4). 2=hA(t,)
Where: 1.-The heat transfer of the deck is not exposed, the heat transfer coefficient of the corresponding heat transfer structure of the shading position is 5.-The heat transfer surface of the shading position is required (see 5.2.3), W/K: The heat transfer surface of the shading position.
, the heat transfer volume from the non-air-conditioned cabin to the air-conditioned light room is calculated according to formula (5), =A
, where: -- heat transfer coefficient of the non-air-conditioned cabin and the air-conditioned light room, w--heat transfer coefficient of the bulkhead between the non-air-conditioned cabin and the air-conditioned light room [5.2.3]. W/mlKA
the total heat transfer product of the adjacent compartments
the source of heat between adjacent rooms (see Table 2)K
, the deck of the heated temporary cabinet
, the middle plate of the corresponding energy
, and the deck of the non-air-conditioned cabin, bulkhead and non-heated tank, cargo hold and similar places. Avoid some of the same and real changes
and, the direction of the yang place
and the use of the place:
- there are symptoms of the toilet with exposed surface
1. The use of the day
: there is an organic clinical or solution to the protection of the veins and the surface of the network and the consideration of the puncture
pay attention to the effectiveness of the external quantity of the internal equipment
1 air conditioning light and control the age of the group between the blood r, K43
5.2.3: extreme, test chain hospital heat junction weak system, the formula (6) is calculated, generally can be registered in the attached A reference material -).
E/T1349—92
In the formula: --- special coefficient of the trapped structure, W/m heat transfer coefficient of the inner and outer surfaces of the air, W/m\K: exposed surface; =8GWmK;
phosphorus surface: e.ew/mK,
—thermal conductivity of each heat-isolating layer, 4;
thermal conductivity of each raw material.w/mK:
M——heat conductivity of each layer (see table s)nK/W:
the contact potential between different material layers, m\K/: positive coefficient of steel structure (see Figure 2).
Material on both sides of the air layer
Both sides are made of two-component material
One is for business thinking change, and the other is for heat light surface
Note that the material needs to be high and wide. 9
5.3 Human body heat through
air layer thickness
.- 1. :
Through the type of research air evidence
Human body heat item is equal to the number of people to help calculate the human body heat weight, and the human body heat and latent base are calculated respectively. According to the single formula (7) calculation.
Human body heat is very, W,
A human body infection potential, W
Human body heat world, W.
Topic: Total heat output per person
Total rest and light activity:
Sensible heat output: 55W
Sensible heat output: 5W
Medium intensity work therapy:
Sensible heat output: 65W
Alarm heat output: 155W
5.4 Lighting heat output
GBT1340992
For cabins with H-light irradiation, the luminous heat base is not included. For cabins without daylight, the lighting heat output is calculated by the formula (). When the ship and relevant agencies do not have the exact lighting wattage, the cabin floor drawing shall be calculated in Table 4, G1=Iw+1.25Fw
or the medium-
sensible quantity, W:
Daylight number, w!
F——number of fluorescent lamps, W,
crew cabins, living rooms, etc.
messaging rooms, public rooms
5.5 Standard quantity of various indoor lighting
number of lighting fixtures per square meter of floor space
number of lighting fixtures
number of heating lamps
number of heating lamps in the cabin (such as wireless communication equipment, automatic door locks, etc.) The heat generation of wireless communication equipment per hour, if not specified, is calculated at 2500W; the heat generation of refrigerators per hour is calculated at 0.3W per cubic meter of heating capacity; electrical equipment such as radios and televisions that are intermittently used, as well as fuel bottles, etc.: For the equipment under consideration, use the coefficient to calculate the power. 5.6 Heat gain in cabin
The heat gain in cabin is calculated according to formula (9):
@@upu-s+a+
wherein,
Cabin net heat gain, W:
Cabin sensible heat, W:
Cabin latent heat, W:
Cabin input heat, W
Human body heat, W,
Lighting heat. Code:
Heat gain from equipment in cabin, W,
Cabin sensible heat = 11 +
Cabin latent heat = 9u.
5.7 Heat loss in cabin in winter
In winter, the heat loss is calculated according to the energy loss, formula (1), d = AAA,4
We collect
The heat loss in the cabin is calculated according to the energy loss, code;
·The difference in internal and external loss or the difference in intensity between the air-conditioned cabin and the non-air-conditioned cabin, K: k——Inner report, the heat transfer integral of the cabin (see 5.2.9). W/m*KA——The heat transfer integral after deducting the area of ​​the glass window and its outer edge, m5
GB/T 13409—92
t,—glass and its 1(Dm cut-out outer circle and the heat coefficient on it, W/n\K; A glass weighs the sum of its 100nur outer complex-graph area, m. 6 Cabin air supply volume distribution and total air volume
6. Cabin air supply distribution plan
The ventilation coefficient of the cabin with specified design parameters shall be calculated according to the larger value of formula (11) and formula (12), and at the same time, it is better to meet the requirements of fresh air disk and air intake.
Ve.28x1.1532T
Formula,V.Xu Zhengbao District Address.m\
V.-c.28RXi.1537
Moreover, the sensible heat of heat in the service risk shall be,; AT seasonal air conditioning supply temperature, the general range is 13 ~ -13K, once connected 1CK@--each dangerous internal heat loss,;
Winter supply air temperature K
For a certain temperature, the temperature parameter is the air supply panel V of the cold sleeping cabin and its ground energy room, which is selected during the air conditioning design. 6.2 Total air conditioning
The total air volume of the air conditioning is calculated according to formula (13).
VEW+EV
In the formula: V-
Total air volume of air conditioning, m/h;
· The wind power supplied by the air conditioner to each air-conditioned cabin/hE(11)
Overflow from the air conditioner to each test room and other cabins subject to the specified temperature and temperature control system as much as possible: : Rise. In order to calculate the heat load of air conditioner multiplied by the total heat load, the summer cooling process is to calculate the inductive load of air conditioner system by formula (1), (4) the total heat load is W, the total sensible heat load, the total latent heat load, W;
d., the heat gain inside is W;
. The wind disturbance heat,
@-the heat gain of air supply air, W
@-the return air temperature rise heat plate, w
Φ-the fresh air heat plate. W
-the air temperature. 1.2kx/
-the constant temperature and humidity of the cabin are limited to the starting part of the cooling cabin. Wind, 1m/- air cooler outlet wind difference, KI/, determined by the total heat load diagram, see Appendix (multiple references). Winter to avoid working sink: total heat load is calculated according to formula (15). ++
In the formula, @—-heat load quotient under heating conditions,
o—internal heat distortion, W:
—heating fresh air point heat, research;
air temperature. =.2kg/m*;
G8/T13409—92
The air volume from the air conditioner to the cabin and other rooms that are not subject to the specified temperature and degree parameters.y
The air volume from the air conditioner heater to the inlet and outlet wind difference is determined by the heat generation and intensity base diagram, see Appendix for reference).
7.1 Heat of air conditioner fan
The heat generated by the motor in the air flow is calculated by the rated power of the motor. The heat generated by the motor outside the air flow is calculated by kPa/m of air temperature, or by formula 16:
-36 center·
In the middle, — heat of air supply fan
I, — total pressure head of fan, Pa
fan windage, m/hl
With total pressure ratio:
— transmission efficiency,
motor transmission: 7.=1-0:
shaft connection: =0.8
triangular belt conversion step:! .35
For fan disk system, the heat generated by the motor is included in the heat range of the fan. 7.2 The air supply is supplied by the air conditioning system with a heat rise plate. The temperature rise limit in the pipe is within 2K. The design calculation is 2K. The overflow rate is calculated according to the formula (8.2 The temperature rise of the air supply pipe in the air supply pipe is taken as W; - total air flow m: 7.3 Air conditioning return air temperature rise potential
Yuan diagnosis machine over the wind system, environmental shadow room wind system, safety temperature production 2K calculation, its temperature rise thermal war formula (13 calculation competition. @286×.1631Vx2
or medium
air conditioning return air temperature rise potential disk, proof:
· total air volume;
fresh air ratio.
7.4 Fresh air disk heat
change season product operating conditions new air volume heat, is the product of fresh air volume and energy internal and external air volume, according to formula (19) calculation, :1.insaov
fresh air quality · W;
α--fresh air ratio:
total air volume mh;
air Demand, 1.2kg/kg,
external design air store value, kJ/kg:
internal design air risk value kJ/kg.
follow the seasonal cooling product fresh air sensible heat mouse safety formula 21 design book. 4.189
p.1.163x0.288aV(.
Wu Zhong:. One new air sensible heat per year,;
fresh air ratio,
total air volume of air conditioning, m/hl
t.-season cabin external design overflow, C;
change season internal ventilation,.
CB/T13409-92
multi-season collection stock sink: heating the new air heat mother according to formula (21) to let brown. -1.163×0. 2RRap1
The excess of fresh air in winter, the proportion of fresh air in the air conditioner, V——total air volume of air conditioner, m\/h
c——air density, 1.2kg/m*
r——initial value of air inside calibration, kJ/kg: t.
iThe external design air station value, hJ/kg is generally taken as 50% of the relative fullness outside. 8 Air conditioning refrigeration equipment health
8.1 Refrigeration equipment design cold water inlet temperature for dangerous restricted navigation areas, 52
For the limited area, the specific decision of each navigation area can be reported: for the central cooling system, the cooling water inlet temperature of the main power equipment design of the ship is uniformly stipulated, 8 .2 Direct air conditioning cooling capacity
Direct air conditioning cooling capacity is calculated according to formula (22), Q:
Where Q: cooling capacity of the cooling unit, kW; @ total heat load, W;
6-3 Indirect air conditioning cooling capacity of water chiller is calculated according to formula (232, 100+9
Center. Water chiller cooling capacity, kW,
@ total heat load, W;
一一 Chilled water system investment, shaft power at the beginning, W. 9 Air circulation and exhaust in the air-conditioned area
9.1 Air circulation in the air-conditioned area
The exhaust air in the air-conditioned area can be used as air conditioning input through the ventilation system or exhaust system. The air-conditioned air in the infirmary, ward, pantry with cooking equipment and smoking room shall not be discharged directly to the outside of the cabin. The air-conditioned air shall be designed as far as possible without recycling. 9.2 Ventilation in the air-conditioned area
Air-conditioned rooms with dirty air in the air-conditioned area shall be equipped with a mechanical exhaust system to discharge the air outside the cabin to maintain the negative pressure inside. For some small places with good natural exhaust conditions, the air intake of the cabin in the air-conditioned area can be used. The air-conditioned air discharged from the air-conditioned cabin or the air can be directly supplied by the air conditioner, or the fresh air can be introduced by the self-heating air intake machine.
GH/T13409—92
9.2.1 If the infirmary and ward have an independent ventilation system connected to the outside, the exhaust volume shall be designed to be 29% larger than the air-conditioned air supply volume. In addition, if the restaurant has an exhaust system directly discharged to the outside, the air supply volume of the air-conditioned cabin can also be partially discharged to the outside of the cabin. 9.2.2 The minimum ventilation frequency for public toilets, public bathrooms, washing rooms, and drying rooms is 15 times. The minimum ventilation frequency for private rooms is 10 times. The minimum ventilation frequency for public rooms on passenger ships is 30 times. 9.2.3 The sum of the air conditioning air removed by each ventilation system in the air-conditioned zone shall not exceed the amount of fresh air supplied to the zone, and together with its return air, it shall not exceed 10% of the air conditioning air supply in the area to maintain the air pressure in the air-conditioned area. 9.24 For the room air conditioning system that does not use stairway return air, the sum of the exhaust air in the air-conditioned zone on each suspended board and the wind turbine shall not exceed 10% of the air supply in the area.
9.2.5 For air-conditioning systems with a large proportion of fresh air or air-conditioning systems with a large proportion of fresh air, if the exhaust system removes less fresh air, a natural exhaust fan should be installed above the appropriate boundary of the air measurement area to prevent the positive air pressure in the area from being too high. 1
GH/T13409—92
Appendix A
Thermal conductivity coefficient of insulation structure and thermal conductivity of materials (safety test materials)
A1 When calculating the heat transfer coefficient of the insulation structure, it is assumed that the cabinet A should be used as the reference. Insulation support, the total heat transfer coefficient of the deck and cabin insulation structure in Table A[, the preliminary calculation should be based on the total heat transfer coefficient of the deck and wall heat limiting structure. Table A1 The total heat transfer coefficient of the deck and wall heat limiting structure. The cabin seat with engine room push-up book. The cabin seat with engine room report. The cabin with boiler protection. The island with boiler protection. The flat panel with light weight of the vehicle. The cargo box with other air-conditioned areas. The cabin with other non-air-conditioned areas. The total heat transfer coefficient of different decks and weak heat exchangers is calculated and checked by A2, which is used as a reference for cabin heat transfer calculation. Table A2 Single board, insulation structure, average total heat transfer coefficient, different values, starting from the order of
Congee mushroom structure
Radial heat structure type
Deck.75mm thick cotton sheet | |tt||Ceiling cabinet; 30, complex grid phase board
Board: 60mm
Beam: 25mm convex cotton
Ceiling Shun: 30 composite boundary cotton cabinet
Deck: 75rans rock root
Wheel, 25oum rock book
No flower: 6mmz board
A city: E3:. Rock heat
: 25mu rock cloth
Closed flower quilt: 6mm Weiou calcium board
Total Nora reduction2 Direct air conditioning cooling capacity
Direct air conditioning cooling capacity is calculated according to formula (22), Q:
Where Q: cooling capacity of the cooling system, kW; @ total heat load, W;
6-3 Indirect air conditioning cooling capacity of water chillers
The cooling capacity of the water chillers is calculated according to formula (232, 100+9
Center. Cooling capacity of the water chiller, kW,
@ total heat load, W;
The shaft power of the chilled water system at the beginning of the project, W. 9 Air circulation and exhaust in the air-conditioned area
9.1 Air in the air-conditioned area The vented air in the air-conditioned area can be used for air conditioning through the ventilation system or exhaust system. The air-conditioned air in the infirmary, ward, pantry with cooking equipment and smoking room shall not be returned to the air conditioning system, but directly discharged to the outside of the cabin. The air-conditioned air shall be designed as far as possible not to be recycled. 9.2 Air conditioning area
There are dirty air spaces in the air-conditioned area, and a mechanical exhaust system shall be installed to discharge the air outside the cabin to maintain the negative pressure inside. Some small rooms with good natural exhaust conditions The air intake of the air-conditioning space can be adjusted by using the self-conditioning air conditioning area, the air-conditioned air discharged from the air-conditioned cabin or the air conditioning directly supplied by the air conditioner, or the fresh air can be introduced by the self-heating air intake machine.
GH/T13409—92
9.2.1 In the hospital, if the ward has an independent ventilation system connected to the outside, the designed exhaust volume is 29% larger than the air conditioning supply volume. In addition, if the restaurant is equipped with an exhaust system directly discharged to the outside, the air conditioning supply volume of the air conditioner can also be partially discharged to the outside of the cabin. 9.2.2 The minimum ventilation frequency for public toilets, public bathrooms, washing rooms, and drying rooms is 15 times. The minimum ventilation frequency for private rooms is 10 times. The minimum ventilation frequency for public rooms on passenger ships is 30 times. 9.2.3 The sum of the air conditioning air removed by each air conditioning system in the air-conditioned zone shall not exceed the amount of fresh air supplied to the zone, and together with its return air volume, it shall not exceed the air conditioning air supply volume of the area to maintain the air pressure in the air-conditioned zone. 9.24 For the room air conditioning system that does not use stairway return air, the use of stratified return air panels shall be Although the exhaust air in the air-conditioned area on the board is equal to the total of the wind turbine, it cannot exceed the correction of the air supply volume in the area.
9.2.5 For air-conditioning systems with a large proportion of fresh air or air-conditioning systems with a large proportion of fresh air, if the exhaust system removes less fresh air, a natural exhaust fan should be installed above the air-conditioning area to prevent the positive air pressure in the area from being too high. 1
GH/T13409—92
Attachment A
Heat transfer coefficient of insulation structure and thermal conductivity of mechanical materials (safety test materials )
A1 When calculating the heat transfer of cabinet A, it is assumed that there is good insulation support. The total heat transfer coefficient of the deck and the whole insulation structure in Table A[, but the preliminary calculation should be based on the total heat transfer coefficient of the deck and wall structure in Table A1, the cabin seat and the engine room, the cabin air conditioning area and the cabin air conditioning area, the cabin air conditioning area and the cabin air conditioning area. The total heat transfer coefficient of the A2 board and the insulation structure of the deck are calculated in the order of different values. 75mm thick cotton
ceiling cabinet; 30, complex grid phase board
board: 60mm
beam: 25mm convex cotton
ceiling: 30 composite boundary cotton cabinet
deck: 75rans rock root
wheel, 25oum rock book
no flower: 6mmz board
A city: E3:. rock heat
: 25mu rock cloth
official quilt: 6mm Weiou calcium board
total Nora reduction2 Direct air conditioning cooling capacity
Direct air conditioning cooling capacity is calculated according to formula (22), Q:
Where Q: cooling capacity of the cooling system, kW; @ total heat load, W;
6-3 Indirect air conditioning cooling capacity of water chillers
The cooling capacity of the water chillers is calculated according to formula (232, 100+9
Center. Cooling capacity of the water chiller, kW,
@ total heat load, W;
The shaft power of the chilled water system at the beginning of the project, W. 9 Air circulation and exhaust in the air-conditioned area
9.1 Air in the air-conditioned area The vented air in the air-conditioned area can be used for air conditioning through the ventilation system or exhaust system. The air-conditioned air in the infirmary, ward, pantry with cooking equipment and smoking room shall not be returned to the air conditioning system, but directly discharged to the outside of the cabin. The air-conditioned air shall be designed as far as possible not to be recycled. 9.2 Air conditioning area
There are dirty air spaces in the air-conditioned area, and a mechanical exhaust system shall be installed to discharge the air outside the cabin to maintain the negative pressure inside. Some small rooms with good natural exhaust conditions The air intake of the air-conditioning space can be adjusted by using the self-conditioning air conditioning area, the air-conditioned air discharged from the air-conditioned cabin or the air conditioning directly supplied by the air conditioner, or the fresh air can be introduced by the self-heating air intake machine.
GH/T13409—92
9.2.1 In the hospital, if the ward has an independent ventilation system connected to the outside, the designed exhaust volume is 29% larger than the air conditioning supply volume. In addition, if the restaurant is equipped with an exhaust system directly discharged to the outside, the air conditioning supply volume of the air conditioner can also be partially discharged to the outside of the cabin. 9.2.2 The minimum ventilation frequency for public toilets, public bathrooms, washing rooms, and drying rooms is 15 times. The minimum ventilation frequency for private rooms is 10 times. The minimum ventilation frequency for public rooms on passenger ships is 30 times. 9.2.3 The sum of the air conditioning air removed by each air conditioning system in the air-conditioned zone shall not exceed the amount of fresh air supplied to the zone, and together with its return air volume, it shall not exceed the air conditioning air supply volume of the area to maintain the air pressure in the air-conditioned zone. 9.24 For the room air conditioning system that does not use stairway return air, the use of stratified return air panels shall be Although the exhaust air in the air-conditioned area on the board is equal to the total of the wind turbine, it cannot exceed the correction of the air supply volume in the area.
9.2.5 For air-conditioning systems with a large proportion of fresh air or air-conditioning systems with a large proportion of fresh air, if the exhaust system removes less fresh air, a natural exhaust fan should be installed above the air-conditioning area to prevent the positive air pressure in the area from being too high. 1
GH/T13409—92
Attachment A
Heat transfer coefficient of insulation structure and thermal conductivity of mechanical materials (safety test materials )
A1 When calculating the heat transfer of cabinet A, it is assumed that there is good insulation support. The total heat transfer coefficient of the deck and the whole insulation structure in Table A[, but the preliminary calculation should be based on the total heat transfer coefficient of the deck and wall structure in Table A1, the cabin seat and the engine room, the cabin air conditioning area and the cabin air conditioning area, the cabin air conditioning area and the cabin air conditioning area. The total heat transfer coefficient of the A2 board and the insulation structure of the deck are calculated in the order of different values. 75mm thick cotton
ceiling cabinet; 30, complex grid phase board
board: 60mm
beam: 25mm convex cotton
ceiling: 30 composite boundary cotton cabinet
deck: 75rans rock root
wheel, 25oum rock book
no flower: 6mmz board
A city: E3:. rock heat
: 25mu rock cloth
official quilt: 6mm Weiou calcium board
total Nora reduction
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