Cooling Load Estimation Report u6q4r
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INDEX SR. NO. 1 2 3 4
CONTENT ACKNOWLEDGEMENT OBJECTIVE TERMINOLOGY SIZING THE SYSTEM
ACKNOWLEDGEMENT
This is to certify that we the team of four students namely Ramkaran khelwar(1208382), Virender kumar (1208415), Vipin chander (1208414) , Shashi kant (1208393) have worked under the able guidance of our mentor and tutor . We are constantly in their touch and received their help and . We heartly recognize and hail there help and without which it wouldn’t be a success.
OBJECTIVE The main aim of our project is:1. To estimate the cooling load for a multi floored building. 2. On the basis of the calculations made , to design a friendly method to find out the cooling load for any given space.
The analysis provides a procedure for preparing a manual calculation for cooling load. A number of published methods, tables and charts from industry handbooks, manufacturer’s engineering data and manufacturer’s catalog data usually provide a good source of design information and criteria in the preparation of the Cooling Load Calculation. It is not the intent of this course to duplicate this information but rather to extract appropriate data from these documents as well as provide a direction regarding the proper use or application of such data so that engineers and designers involved in preparing the calculations can make the appropriate decision and/or apply proper engineering judgment. The analysis includes two example calculations for better understanding and for the partial fulfillment of the subject.
TERMINOLOGY
Commonly used relative to heat transmission and load calculations are defined below in accordance with ASHRAE Standard , Refrigeration and Definitions. Space – is either a volume or a site without a partition or a partitioned room or group of rooms. Room – is an enclosed or partitioned space that is usually treated as single load. Zone – is a space or group of spaces within a building with heating and/or cooling requirements sufficiently similar so that comfort conditions can be maintained throughout by a single controlling device. Sensible Heat Gain – is the energy added to the space by conduction, convection and/or radiation. Latent Heat Gain – is the energy added to the space when moisture is added to the space by means of vapor emitted by the occupants, generated by a process or through air infiltration from outside or adjacent areas. Radiant Heat Gain – the rate at which heat absorbed is by the surfaces enclosing the space and the objects within the space. Space Heat Gain – is the rate at which heat enters into and/or is generated within the conditioned space during a given time interval. Space Cooling Load – is the rate at which energy must be removed from a space to maintain a constant space air temperature. Space Heat Extraction Rate - the rate at which heat is removed from the conditioned space and is equal to the space cooling load if the room temperature remains constant. Temperature, Dry Bulb – is the temperature of air indicated by a regular thermometer.
Temperature, Wet Bulb – is the temperature measured by a thermometer that has a bulb wrapped in wet cloth. The evaporation of water from the thermometer has a cooling effect, so the temperature indicated by the wet bulb thermometer is less than the temperature indicated by a dry-bulb (normal, unmodified) thermometer. The rate of evaporation from the wet-bulb thermometer depends on the humidity of the air. Evaporation is slower when the air is already full of water vapor. For this reason, the difference in the temperatures indicated by ordinary dry bulb and wet bulb thermometers gives a measure of atmospheric humidity. Temperature, Dewpoint – is the temperature to which air must be cooled in order to reach saturation or at which the condensation of water vapor in a space begins for a given state of humidity and pressure. Relative humidity - describes how far the air is from saturation. It is a useful term for expressing the amount of water vapor when discussing the amount and rate of evaporation. One way to approach saturation, a relative humidity of 100%, is to cool the air. It is therefore useful to know how much the air needs to be cooled to reach saturation. Thermal Transmittance or Heat Transfer Coefficient (U-factor) – is the rate of heat flow through a unit area of building envelope material or assembly, including its boundary films, per unit of temperature difference between the inside and outside air.
SIZING YOUR AIR-CONDITIONING SYSTEM
Concepts and fundamentals of air conditioner sizing is based on heat gain, and/or losses in a building. It is obvious that you will need to remove the amount of heat gain - if it is hot outside. Similarly, you'll need to add in the heat loss from your space - if outside temperature is cold. In short, heat gain and loss, must be equally balanced by heat removal, and addition, to get the desired room comfort that we want. The heat gain or heat loss through a building depends on: a. The temperature difference between outside temperature and our desired temperature. b. The type of construction and the amount of insulation is in your ceiling and walls. Let's say, that you have two identical buildings, one is build out of glass, and the other out of brick. Of course the one built with glass would require much more heat addition, or removal, compared to the other - given a same day. This is because the glass has a high thermal conductivity (U-value) as compared to the brick and also because it is transparent, it allows direct transmission of solar heat. c. How much shade is on your building’s windows, walls, and roof? Two identical buildings with different orientation with respect to the direction of sun rise and fall will also influence the air conditioner sizing. d. How large is your room? The surface area of the walls. The larger the surface area - the more heat can loose, or gain through it. e. How much air leaks into indoor space from the outside? Infiltration plays a part in determining our air conditioner sizing. Door gaps, cracked windows, chimneys - are the "doorways" for air to enter from outside, into your living space. f. The occupants. It takes a lot to cool a town hall full of people. g. Activities and other equipment within a building. Cooking? Hot bath? Gymnasium?
h. Amount of lighting in the room. High efficiency lighting fixtures generate less heat. i. How much heat the appliances generate. Number of power equipments such as oven, washing machine, computers, TV inside the space; all contribute to heat. The air conditioner's efficiency, performance, durability, and cost depend on matching its size to the above factors. Many designers use a simple square foot method for sizing the airconditioners. The most common rule of thumb is to use "1 ton for every 500 square feet of floor area". Such a method is useful in preliminary estimation of the equipment size. The main drawback of rules-of-thumb methods is the presumption that the building design will not make any difference. Thus the rules for a badly designed building are typically the same as for a good design. It is important to use the correct procedure for estimating heat gain or heat loss. Two groups— the Air Conditioning Contractors of America (ACCA) and the American Society of Heating, Refrigerating, and Air Conditioning Engineers (ASHRAE)—publish calculation procedures for sizing central air conditioners.
HEAT FLOW RATES
In air-conditioning design, four related heat flow rates, each of which varies with time, must be differentiated: a. Space heat gain ----------------How much heat (energy) is entering the space? b. Space cooling load -------------How much energy must be removed from the space to keep temperature and relative humidity constant? c. Space heat extraction-----------How much energy is the HVAC removing from the space? d. Cooling load (coil) ---------------How much energy is removed by the cooling coil serving various space plus any loads external to the spaces such as duct heat gain, duct leakage, fan heat and outdoor makeup air?
Space Heat Gain This instantaneous rate of heat gain is the rate at which heat enters into and/or is generated within a space at a given instant. Heat gain is classified by: The manner in which it enters the space – a. Solar radiation through transparent surfaces such as windows b. Heat conduction through exterior walls and roofs c. Heat conduction through interior partitions, ceilings and floors d. Heat generated within the space by occupants, lights, appliances, equipment and processes e. Loads as a result of ventilation and infiltration of outdoor air f. Other miscellaneous heat gains
Whether it is a sensible or latent gain -Sensible heat - Heat which a substance absorbs, and while its temperature goes up, the substance does not change state. Sensible heat gain is directly added to the conditioned space by conduction, convection, and/or radiation. Note that the sensible heat gain entering the conditioned space does not equal the sensible cooling load during the same time interval because of the stored heat in the building envelope. Only the convective heat becomes cooling load instantaneously. Sensible heat load is total of:a. Heat transmitted thru floors, ceilings, walls b. Occupant’s body heat c. Appliance & Light heat d. Solar Heat gain thru glass e. Infiltration of outside air f. Air introduced by Ventilation
Latent Heat Loads - Latent heat gain occurs when moisture is added to the space either from internal sources (e.g. vapor emitted by occupants and equipment) or from outdoor air as a result of infiltration or ventilation to maintain proper indoor air quality. Latent heat load is total of :a. Moisture-laden outside air form Infiltration & Ventilation b. Occupant Respiration & Activities c. Moisture from Equipment & Appliances
To maintain a constant humidity ratio, water vapor must condense on cooling apparatus at a rate equal to its rate of addition into the space. This process is called dehumidification and is very energy intensive, for instance, removing 1 kg of humidity requires approximately 0.7 kWh of energy. Space Heat Gain V/s Cooling Load (Heat Storage Effect)
Space Heat Gain is ≠ to Space Cooling Load The heat received from the heat sources (conduction, convection, solar radiation, lightning, people, equipment, etc.) does not go immediately to heating the room air. Only some portion of it is absorbed by the air in the conditioned space instantaneously leading to a minute change in its temperature. Most of the radiation heat especially from sun, lighting, people is first absorbed by the internal surfaces, which include ceiling, floor, internal walls, furniture etc. Due to the large but finite thermal capacity of the roof, floor, walls etc., their temperature increases slowly due to absorption of radiant heat. The radiant portion introduces a time lag and also a decrement factor depending upon the dynamic characteristics of the surfaces. Due to the time lag, the effect of radiation will be felt even when the source of radiation, in this case the sun is removed.
Differences between Space Heat Gain and Space Cooling Load Differences between instantaneous heat gain and cooling load is due to heat storage affect. The relation between heat gain and cooling load and the effect of the mass of the structure (light, medium & heavy) is shown below. From the figure it is evident that, there is a delay in the peak heat, especially for heavy construction.
DESIGN INFORMATION
To calculate the space cooling load, detailed building information, location, site and weather data, internal design information and operating schedules are required. Information regarding the outdoor design conditions and desired indoor conditions are the starting point for the load calculation and is discussed below. Outdoor Design Weather Conditions ASHRAE Handbook Fundamentals list tables of climate conditions : In these tables: The information provided in table 1a, 2a and 3a are for heating design conditions that include: a. Dry bulb temperatures corresponding to 99.6% and 99% annual cumulative frequency of occurrence b. Wind speeds corresponding to 1%, 2.5% and 5% annual cumulative frequency of occurrence, c. Wind direction most frequently occurring with 99.6% and 0.4% dry-bulb temperatures. d. Average of annual extreme maximum and minimum dry-bulb temperatures and standard deviations. The information provided in table 1b, 2b and 3b are for cooling and humidity control conditions that include: a. Dry bulb temperature corresponding to 0.4%, 1.0% and 2.0% annual cumulative frequency of occurrence and the mean coincident wet-bulb temperature (warm). These conditions appear in sets of dry bulb (DB) temperature and the mean coincident wet bulb (MWB) temperature since both values are needed to determine the sensible and latent (dehumidification) loads in the cooling mode.
b. Wet-bulb temperature corresponding to 0.4%, 1.0% and 2.0% annual cumulative frequency of occurrence and the mean coincident dry-bulb temperature c. Dew-point temperature corresponding to 0.4%, 1.0% and 2.0% annual cumulative frequency of occurrence and the mean coincident dry-bulb temperature and humidity ratio (calculated for the dew-point temperature at the standard atmospheric pressure at the elevation of the station). d. Mean daily range (DR) of the dry bulb temperature, which is the mean of the temperature difference between daily maximum and minimum temperatures for the warmest month (highest average dry-bulb temperature). These are used to correct CLTD values. In choosing the HVAC outdoor design conditions, it is neither economical nor practical to design equipment either for the annual hottest temperature or annual minimum temperature, since the peak or the lowest temperatures may occur only for a few hours over the span of several years. Economically speaking short duration peaks above the system capacity might be tolerated at significant reductions in first cost; this is a simple risk - benefit decision for each building design. Therefore, as a practice, the ‘design temperature and humidity’ conditions are based on frequency of occurrence. The summer design conditions have been presented for annual percentile values of 0.4, 1 and 2% and winter month conditions are based on annual percentiles of 99.6 and 99%. The term “design condition” refers to the %age of time in a year (8760 hours), the values of dry-bulb, dew-point and wet-bulb temperature exceed by the indicated percentage. The 0.4%, 1.0%, 2.0% and 5.0% values are exceeded on average by 35, 88, 175 and 438 hours. The 99% and 99.6% cold values are defined in the same way but are viewed as the values for which the corresponding weather element are less than the design condition 88 and 35 hours, respectively. 99.6% value suggests that the outdoor temperature is equal to or lower than design data 0.4% of the time.
Design condition is used to calculate maximum heat gain and maximum heat loss of the building. For comfort cooling, use of the 2.5% occurrence and for heating use of 99% values is recommended. The 2.5% design condition means that the outside summer temperature and coincident air moisture content will be exceeded only 2.5% of hours from June to September or 73 out of 2928 hours (of these summer months) i.e. 2.5% of the time in a year, the outdoor air temperature will be above the design condition.
BUILDING CHARACTERISTICS
To calculate space heat gain, the following information on building envelope is required: a. Architectural plans, sections and elevations – for estimating building dimensions/area/volume b. Building orientation (N, S, E, W, NE, SE, SW, NW, etc), location etc c. External/Internal shading, ground reflectance etc. d. Materials of construction for external walls, roofs, windows, doors, internal walls, partitions, ceiling, insulating materials and thick nesses, external wall and roof colors - select and/or compute U-values for walls, roof, windows, doors, partitions, etc. Check if the structure is insulated and/or exposed to high wind. e. Amount of glass, type and shading on windows
OPERATING SCHEDULES
Obtain the schedule of occupants, lighting, equipment, appliances, and processes that contribute to the internal loads and determine whether air conditioning equipment will be operated continuously or intermittently (such as, shut down during off periods, night setback, and weekend shutdown). Gather the following information: • Lighting requirements, types of lighting fixtures • Appliances requirements such as computers, printers, fax machines, water coolers, refrigerators, microwave, miscellaneous electrical s, cables etc • Heat released by the Cooling equipment. • Number of occupants, time of building occupancy and type of building occupancy
COOLING LOAD METHODOLOGY – CONSIDERATIONS & ASSUMPTIONS
Design cooling load takes into all the loads experienced by a building under a specific set of assumed conditions. The assumptions behind design cooling load are as follows: a. Weather conditions are selected from a long-term statistical database. The conditions will not necessary represent any actual year, but are representative of the location of the building. ASHRAE has tabulated such data. b. The solar loads on the building are assumed to be those that would occur on a clear day in the month chosen for the calculations. c. The building occupancy is assumed to be at full design capacity.
d. The ventilation rates are either assumed on air changes or based on maximum occupancy expected. e. All building equipment and appliances are considered to be operating at a reasonably representative capacity. f. Lights and appliances are assumed to be operating as expected for a typical day of design occupancy. g. Latent as well as sensible loads are considered. h. Heat flow is analyzed assuming dynamic conditions, which means that heat storage in building envelope and interior materials is considered. i. The latent heat gain is assumed to become cooling load instantly, whereas the sensible heat gain is partially delayed depending on the characteristics of the conditioned space. According to the ASHRAE regulations, the sensible heat gain from people is assumed 30% convection (instant cooling load) and 70% radiative (delayed portion). j. Peak load calculations evaluate the maximum load to size and select the refrigeration equipment. The energy analysis program compares the total energy use in a certain period with various alternatives in order to determine the optimum one. k. Space (zone) cooling load is used to calculate the supply volume flow rate and to determine the size of the air system, ducts, terminals, and diffs. The coil load is used to determine the size of the cooling coil and the refrigeration system. Space cooling load is a component of the cooling coil load. l. The heat transfer due to ventilation is not a load on the building but a load on the system.
CLTD/SCL/CLF METHOD OF LOAD CALCULATION (ASHRAE FUNDAMENTALS 1997)
As mentioned before, the heat gain to the building is not converted to cooling load instantaneously. CLTD (cooling load temperature difference), SCL (solar cooling load factor), and CLF (cooling load factor): all include the effect of (1) time-lag in conductive heat gain through opaque exterior surfaces and (2) time delay by thermal storage in converting radiant heat gain to cooling load. This approach allows cooling load to be calculated manually by use of simple multiplication factors. a. CLTD is a theoretical temperature difference that s for the combined effects of inside and outside air temp difference, daily temp range, solar raiation and heat storage in the construction assembly/building mass. It is affected by orientation, tilt, month, day, hour, latitude, etc. CLTD factors are used for adjustment to conductive heat gains from walls, roof, floor and glass. b. CLF s for the fact that all the radiant energy that enters the conditioned space at a particular time does not become a part of the cooling load instantly. The CLF values for various surfaces have been calculated as functions of solar time and orientation and are available in the form of tables in ASHRAE Handbooks. CLF factors are used for adjustm ent to heat gains from internal loads such as lights, occupancy, power appliances. c. SCL factors are used for adjustment to transmission heat gains from glass.
DIMENSIONS OF SPACE (LECTURE HALLS)
NO OF DOORS
:-
2
•
WIDTH
:-
0.95 m
•
LENGTH
:-
2.11 m
•
THICKNESS
:-
0.032 m
•
AREA
:-
2.0045 m^2
•
THERMAL CONDUCTIVITY
:-
.09 W/mK
NO. OF WINDOW
:-
3
•
WIDTH
:-
2.33 m
•
HEIGHT
:-
2.17 m
•
AREA
:-
5.0561 m^2
•
THICKNESS
:-
0.005 m
•
THERMAL CONDUCTIVITY (GLASS)
:-
.78 W/mk
PARTITION .33m (Brick thickness =0.28m
ROOM SPACE •
WIDTH
:-
8.10 m
•
LENGTH
:-
9.70 m
•
HEIGHT
:-
3.50 m
•
VOLUME OF SPACE
•
THICKNESS OF WALL
•
Plaster (Inside + Outside)
:-
0.05 m
•
Roof construction
:-
0.20 m (concrete)
•
THERMAL CONDUCTIVITY (CONCRETE) :-
.73W/mK
•
THERMAL CONDUCTIVITY (BRICK)
:-
1.32W/mK
•
THERMAL CONDUCTIVITY (PLASTER)
:-
.48W/mK
•
THERMAL CONDUCTIVITY (WOOD)
:-
.09W/mK
::-
274.995 m^3 .22m(east , west ; Brick thickness=0.20m)
FILM COEFFICIENT
F(o) F (i)
::-
23 W/m^2K 7 W/m^2K
INTERNAL LOAD FACTOR NO. OF TUBES
:-
6 ( 20 W EACH =120 WATT)
NO. OF FANS
:-
7 ( 40 W EACH =280 WATT)
TOTAL
:-
400 WATT
NO. OF OCCUPANTS
:-
61
CALCULATION FOR OVERALL THERMAL CO-EFFICENT FOR OUTSIDE AND INSIDE WALL WALL 1/U= 1/23 + .05/0.48 + 0.15/1.73 + 1/7 (OUTER FILM+ PLASTER+ BRICK+
INSIDE FILM)
U=2.47 W/m^2K
FOR PARTITION WALL 1/U = 1/7 + 0.05/0.48 + 0.28/1.32 + 1/7 (INSIDE + PLASTER + BRICK + INSIDE) U=1.66 W/m^2K
FOR ROOF AND FLOOR 1/U = 1/7 + 0.05/0.48 + 0.20/1.73 + 1/7 (INSIDE + PLASTER + CONCRETE + INSIDE) U=1.64W/m^2K
WINDOW GLASS 1/U = 1/23 + 0.005/0.78 + 1/7 U = 5.208
DOOR 1/U = 1/23 + 0.032/0.09 + 1/7 U=1.84
Area of East wall=31.88 m^2
Area of West wall=20.72 m^2
Area of partition =29.97 m^2
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 1) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST GLASS
15.17
232.92
---
3533.48
WEST WALL
20.72
18
2.47
921.21
EAST DOOR
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
NORTH WALL
29.97
12
2.47
888.31
FLOOR
98.57
2.5
1.64
404.14
PARTITION
29.97
0
1.66
0
ROOF
98.57
0
1.97
0
INFILTRATION 19.8cmm
18
20.4
7270
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = (18433.48 + 9240) W = 27673.86 W = 7.87 TR
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 2,3,4) ITEM
AREA(m^2)
WEST GLASS
15.17
∂T/∂ф/Sun Gain
FACTOR
232.92
---
W 3533.39
WEST WALL
20.72
18
2.47
921.21
EAST DOOR
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
FLOOR
98.57
2.5
1.64
404.14
PARTITION
29.97
0
1.66
0
PARTITION
29.97
0
1.66
0
ROOF
98.57
0
1.97
0
18
20.4
INFILTRATION 19.8cmm
7270
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = 3*(17545.46 + 9240) W = 3*26785.46 W = 80356.38 W = 22.85 TR
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 5) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST GLASS
15.17
232.92
---
3533.39
WEST WALL
20.72
18
2.47
921.21
EAST DOOR
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
FLOOR
98.57
2.5
1.64
404.14
PARTITION
29.97
0
1.66
0
PARTITION
29.97
8
1.66
398
ROOF
98.57
0
1.97
0
INFILTRATION 19.8cmm
18
20.4
7270
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = (17943.46 + 9240) W = 27183.46 W = 7.73TR
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 6,11) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST GLASS
15.17
232.92
---
3533.39
WEST WALL
20.72
18
2.47
921.21
EAST DOOR
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
NORTH WALL
29.97
12
2.47
888.31
FLOOR
98.57
0
1.64
0
0
1.66
PARTITION
29.97
0
ROOF
98.57
0
1.97
0
INFILTRATION 19.8cmm
18
20.4
7270
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = 2*(18029.37 + 9240) W = 2*27269.37 W = 54538.74 W = 15.51 TR
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 7,8,9,12,13,14) ITEM
AREA(m^2)
WEST GLASS
15.17
∂T/∂ф/Sun Gain
FACTOR
232.92
---
W 3111.49
WEST WALL
20.72
18
2.47
921.21
EAST DOOR
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
FLOOR
98.57
0
1.64
0
PARTITION
29.97
0
1.66
0
PARTITION
29.97
0
1.66
0
ROOF
98.57
0
1.97
0
18
20.4
7270
INFILTRATION 19.8cmm
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = 6*(17141.32 + 9240) W = 6*26381.32 W = 158287.92 W = 45.01 TR
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 10,15) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST GLASS
15.17
232.92
---
3533.40
WEST WALL
20.72
18
2.47
921.21
EAST DOOR
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
FLOOR
98.57
0
1.64
0
PARTITION
29.97
0
1.66
0
PARTITION
29.97
8
1.66
398
ROOF
98.57
0
1.97
0
18
20.4
7270
INFILTRATION 19.8cmm
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = 2*(17539.46 + 9240) W = 2*26779.46 W = 53558.92 W = 15.23 TR
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 16) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST GLASS
15.17
232.92
---
3533.49
WEST WALL
20.72
18
2.47
921.21
EAST DOOR
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
NORTH WALL
29.97
12
2.47
888.31
FLOOR
98.57
0
1.64
0
PARTITION
29.97
0
1.66
0
ROOF
98.57
18
1.97
3495.29
INFILTRATION 19.8cmm
18
20.4
7270
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = (21524.92 + 9240) W = 30764.92 W = 8.75 TR
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 17,18,19) ITEM
AREA(m^2)
WEST GLASS
15.17
∂T/∂ф/Sun Gain
FACTOR
232.92
---
W 3533.49
WEST WALL
20.72
18
2.47
921.21
EAST DOOR
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
FLOOR
98.57
0
1.64
0
PARTITION
29.97
0
1.66
0
PARTITION
29.97
0
1.66
0
ROOF
98.57
18
1.97
3495.29
INFILTRATION 19.8cmm
18
20.4
7270
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = 3*(20636.61 + 9240) W = 3*29876.61 W = 89629.83 W = 25.49 TR
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 20) ITEM
AREA(m^2)
WEST GLASS
15.17
WEST WALL
20.72
EAST DOOR
∂T/∂ф/Sun Gain
FACTOR
232.92
W
---
3533.49
18
2.47
921.21
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
FLOOR
98.57
0
1.64
0
PARTITION
29.97
0
1.66
0
PARTITION
29.97
8
1.66
398
ROOF
98.57
18
1.97
3495.29
INFILTRATION 19.8cmm
18
20.4
7270
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = (21034.61 + 9240) W = 30274.61 W = 8.61 TR
DIMENSIONS OF SPACE (TEACHERS’ ROOMS)
NO OF DOORS
:-
1
•
WIDTH
:-
0.95 m
•
LENGTH
:-
2.11 m
•
THICKNESS
:-
0.032 m
•
AREA
:-
2.0045 m^2
•
THERMAL CONDUCTIVITY
:-
.09 W/mK
NO. OF WINDOW
:-
1
•
WIDTH
:-
2.33 m
•
HEIGHT
:-
2.17 m
•
AREA
:-
5.0561 m^2
•
THICKNESS
:-
0.005 m
•
THERMAL CONDUCTIVITY (GLASS)
:-
.78 W/mk
PARTITION .33m (Brick thickness =0.28m)
ROOM SPACE •
WIDTH
:-
2.26 m
•
LENGTH
:-
2.4 m
•
HEIGHT
:-
3.50 m
•
VOLUME OF SPACE
:-
18.984 m^3
•
THICKNESS OF WALL
•
Plaster (Inside + Outside)
:-
0.05 m
•
Roof construction
:-
0.20 m (concrete)
•
THERMAL CONDUCTIVITY (CONCRETE) :-
.73W/mK
•
THERMAL CONDUCTIVITY (BRICK)
:-
1.32W/mK
•
THERMAL CONDUCTIVITY (PLASTER)
:-
.48W/mK
•
THERMAL CONDUCTIVITY (WOOD)
:-
.09W/mK
:-
.22m(east , west ; Brick thickness=0.20m)
FILM COEFFICIENT
F(o) F (i)
::-
23 W/m^2K 7 W/m^2K
INTERNAL LOAD FACTOR NO. OF TUBES
:-
1 ( 20 WATT )
NO. OF FANS
:-
1 ( 40 WATT )
TOTAL
:-
60 WATT
NO. OF OCCUPANTS
:-
2
Area of East/West Wall=7.91 m^2
Area of North/South Wall=3.3 m^2 / 8.4m^2
Area of partition =7.91 m^2
LOAD CALCULATION (SENSIBLE HEAT)
(Teachers’ Room 1,5,6,10)
ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST/EAST WALL 7.91
6
2.47
117.23
DOOR
0
1.84
0
12
2.47
888.31
1.64
22.22
2.004
NORTH/SOUTH WALL 29.97 FLOOR
5.42
2.5
PARTITION
7.91
0
1.66
0
ROOF
5.42
0
1.97
0
--
--
INFILTRATION 19.8cmm
2120
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
2
75
150
TUBES
1
20
20
FAN
1
40
40
EXTRA USAGE
--
--
300
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
2
_
55
110
TOTAL LOAD TOTAL LOAD = SHL + LHL = 4*(3657.76 + 6050) W = 4*9707.76 W = 38831.04 W = 11.04 TR
LOAD CALCULATION (SENSIBLE HEAT) (Teachers’ Room 2,3,4,7,8,9) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST/EAST WALL 7.91
0
2.47
0
DOOR
0
1.84
0
12
2.47
888.31
1.64
22.22
2.004
NORTH/SOUTH WALL 29.97 FLOOR
5.42
2.5
PARTITION
7.91
0
1.66
0
ROOF
5.42
0
1.97
0
--
--
INFILTRATION 19.8cmm
2120
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
2
75
150
TUBES
1
20
20
FAN
1
40
40
EXTRA USAGE
--
--
300
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
2
_
55
110
TOTAL LOAD TOTAL LOAD = SHL + LHL = 6*(3540.53 + 6050) W = 6*9590.53 W = 57543.18 W = 16.37 TR
LOAD CALCULATION (SENSIBLE HEAT) (Teachers’ Room 11,15,16,20,21,25,26,30) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST/EAST WALL 7.91
6
2.47
117.23
DOOR
0
1.84
0
NORTH/SOUTH WALL 29.97
12
2.47
888.31
FLOOR
5.42
0
1.64
0
PARTITION
7.91
0
1.66
0
ROOF
5.42
0
1.97
0
--
--
2.004
INFILTRATION 19.8cmm
2120
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
2
75
150
TUBES
1
20
20
FAN
1
40
40
EXTRA USAGE
--
--
300
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
2
_
55
110
TOTAL LOAD TOTAL LOAD = SHL + LHL = 8*(3635.54 + 6050) W = 8*9685.54 W = 76884.32 W = 21.87 TR
LOAD CALCULATION (SENSIBLE HEAT) (Teachers’ Room 12,13,14,17,18,19,22,23,24,27,28,29) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST/EAST WALL 7.91
0
2.47
0
DOOR
0
1.84
0
NORTH/SOUTH WALL 29.97
12
2.47
888.31
FLOOR
5.42
0
1.64
0
PARTITION
7.91
0
1.66
0
ROOF
5.42
0
1.97
0
2.004
INFILTRATION 19.8cmm
--
--
2120
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
2
75
150
TUBES
1
20
20
FAN
1
40
40
EXTRA USAGE
--
--
300
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
2
_
55
110
TOTAL LOAD TOTAL LOAD = SHL + LHL = 12*(3518.31 + 6050) W = 12*9568.31 W = 113019.72 W = 32.14 TR
DIMENSIONS OF SPACE (H.O.D. ROOMS)
NO OF DOORS
:-
1
•
WIDTH
:-
0.95 m
•
LENGTH
:-
2.11 m
•
THICKNESS
:-
0.032 m
•
AREA
:-
2.0045 m^2
•
THERMAL CONDUCTIVITY
:-
.09 W/mK
PARTITION .33m (Brick thickness =0.28m)
ROOM SPACE •
WIDTH
:-
4.52 m
•
LENGTH
:-
2.4 m
•
HEIGHT
:-
3.50 m
•
VOLUME OF SPACE
:-
37.968 m^3
•
THICKNESS OF WALL
•
Plaster (Inside + Outside)
:-
0.05 m
•
Roof construction
:-
0.20 m (concrete)
:-
.22m(east , west ; Brick thickness=0.20m)
FILM COEFFICIENT
F(o) F (i)
::-
23 W/m^2K 7 W/m^2K
INTERNAL LOAD FACTOR NO. OF TUBES
:-
2 ( 20 WATT EACH, = 40W )
NO. OF FANS
:-
1 ( 40 WATT )
TOTAL
:-
80 WATT
NO. OF OCCUPANTS
:-
3
Area of East Wall=15.82 m^2
Area of North Wall=8.4m^2
Area of partition =15.82 m^2
Area of South Wall =6.4 m^2
Floor Area =10.85 m^2
LOAD CALCULATION (SENSIBLE HEAT) (H.O.D. Room, Ground Floor) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
EAST WALL
15.82
6
2.47
234.45
DOOR
2.004
6
1.84
22.12
NORTH WALL
8.4
18
2.47
373.46
10.85
2.5
1.64
44.5
6
1.66
157.56
0
1.97
FLOOR PARTITION ROOF
15.82 10.85
INFILTRATION 19.8cmm
--
--
SOUTH WALL
6
2.47
6.4
0 2120 94.85
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
3
75
225
TUBES
2
20
40
FAN
1
40
40
EXTRA USAGE
--
--
500
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
3
_
55
165
TOTAL LOAD TOTAL LOAD = SHL + LHL = (3851.94 + 6105) W = 9956.94 W = 2.83 TR
LOAD CALCULATION (SENSIBLE HEAT) (H.O.D. Room First Floor,Second Floor) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
EAST WALL
15.82
6
2.47
234.45
DOOR
2.004
6
1.84
22.12
NORTH WALL
8.4
18
2.47
373.46
10.85
0
1.64
0
6
1.66
157.56
0
1.97
FLOOR PARTITION ROOF
15.82 10.85
INFILTRATION 19.8cmm
--
--
SOUTH WALL
6
2.47
6.4
0 2120 94.85
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
3
75
225
TUBES
2
20
40
FAN
1
40
40
EXTRA USAGE
--
--
500
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
3
_
55
165
TOTAL LOAD TOTAL LOAD = SHL + LHL = 2*(3807.44 + 6105) W = 2*9912.44 W = 19824.88 W = 5.64 TR
LOAD CALCULATION (SENSIBLE HEAT) (H.O.D. Room Top Floor) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
EAST WALL
15.82
6
2.47
234.45
DOOR
2.004
6
1.84
22.12
NORTH WALL
8.4
18
2.47
373.46
10.85
0
1.64
0
6
1.66
157.56
18
1.97
384.74
FLOOR PARTITION ROOF
15.82 10.85
INFILTRATION 19.8cmm
--
--
SOUTH WALL
6
2.47
6.4
2120 94.85
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
3
75
225
TUBES
2
20
40
FAN
1
40
40
EXTRA USAGE
--
--
500
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
3
_
55
165
TOTAL LOAD TOTAL LOAD = SHL + LHL = (4192.18 + 6105) W = 10297.18 W = 2.93 TR
PROGRAM FILE FOR THE FRIENDLY SOFTWARE FOR FINDING OUT THE COOLING LOAD OF ANY GIVEN SPACE OF KNOWN DATA
#include<stdio.h> #include
void main() { float dbt,wbt,wd,ar_roof,tppw,tbpw,inf_fac,power,hd,td,csad,th_cn_d,th_cn_c,th_cn_p,th_cn_b,th_ cn_g,ww,hw,tw,csaw,wrs,hrs,lrs,volr,csa_wal,tbw,tpw,tcr,tpr,watt,u_wall,u_part,u_roof,u_floo r,u_wndw,u_door,ar_ewal,ar_wwal,ar_part,shl_wg,shl_ww,shl_edr,shl_ew,shl_par,shl_roof,shl _floor,shl_inf,shl_ppl,shl_eqp,lhl_inf,lhl_ppl,lhl,shl,thl,tl;
int doors,tubes,ppl=60,fans,wndws; clrscr(); printf("\n\n\t\tCOOLING LOAD ESTIMATION FOR A SINGLE ROOM"); printf("\t\n\nEnter the outside dry bulb temprature in degree celsius:"); scanf("%f",&dbt); printf("\t\n\nEnter the outside wet bulb temprature in degree celsius:"); scanf("%f",&wbt);
if(wbt>dbt) { printf("\n\n\tDry bulb temp. can never be less than Wet bulb temp."); } else { printf("\n\nThe inside comfort conditions being used are ::\n\n\tInner Dry Bulb Temprature(in degree C) = 25\n\n\tRelative Humidity = 50 %"); printf("\n\nThe capacity of the room is taken as 60"); printf("\n\nEnter the details of the Room::"); printf("\n\n\No. of Doors::"); scanf("%d",&doors); printf("\n\nWidth, Height and Thickness of door(m) ::"); scanf("%f%f%f",&wd,&hd,&td); csad=wd*hd*doors; printf("\n\nThe total door area(sq. m) is :: %f",csad); printf("\n\n\tREFER TO APPENDIX 1 FOR THERMAL CONDUCTIVITY OF MATERIALS"); printf("\n\nEnter the thermal conductivity of door material(W/mK) ::"); scanf("%f",&th_cn_d); printf("\n\nNo. of Windows :: ");
scanf("%d",&wndws); printf("\n\nWidth, Height and Thickness of glass used in windows(m) :: "); scanf("%f%f%f",&ww,&hw,&tw); csaw=ww*hw*wndws; printf("\n\nThe total cross sectional area of the windows(sq. m) is %f",csaw); printf("\n\nEnter the thermal conductivity of glass used for windows(W/mK) ::"); scanf("%f",&th_cn_g); printf("\n\nEnter the dimensions of the room space(in m) :: "); printf("\n\nWidth, Length and Height :: "); scanf("%f%f%f",&wrs,&lrs,&hrs); volr=wrs*lrs*hrs; ar_roof=wrs*lrs; csa_wal=lrs*hrs; printf("\n\nThe volume of the room(cu. m) is %f",volr); printf("\n\nEnter the total thickness of brick material in the wall(m) ::"); scanf("%f",&tbw); printf("\n\nEnter the thermal conductivity of brick material used(W/mK) ::"); scanf("%f",&th_cn_b); printf("\n\nEnter the thickness of plaster being used(m) ::"); scanf("%f",tpw);
printf("\n\nEnter the thermal conductivity of plaster used in the wall(W/mK) ::"); scanf("%f",&th_cn_p); printf("\n\nEnter the total thickness of concrete material used in the roof(m) ::"); scanf("%f",&tcr); printf("\n\nEnter the thermal conductivity of the concrete material used(W/mK) ::"); scanf("%f",&th_cn_c); tpr=tpw; tppw=tpw; printf("\n\nEnter the total thickness of brick material in the partition wall(m) ::"); scanf("%f",tbpw); printf("\n\nNo. of 20W tubelights used in the room ::"); scanf("%f",tubes); printf("\n\nNo. of 40W fans used in the room ::"); scanf("%d",fans); printf("\n\nThe Total Wattage of all the other equipments used in the room ::"); scanf("%f",&watt); power=(20.0*tubes)+(40.0*fans)+watt;
u_wall=1.0/((1.0/23.0)+(tpw/th_cn_p)+(tbw/th_cn_b)+(1.0/7.0)); u_part=1.0/((2.0/7.0)+(tppw/th_cn_p)+(tbpw/th_cn_b)); u_roof=1.0/((2.0/7.0)+(tpr/th_cn_p)+(tcr/th_cn_c)); u_floor=u_roof; u_wndw=1.0/((1.0/23.0)+(1.0/7.0)+(tw/th_cn_g)); u_door=1.0/((1.0/23.0)+(1.0/7.0)+(td/th_cn_d)); ar_ewal=csa_wal-csad; ar_wwal=csa_wal-csaw; ar_part=wrs*hrs; shl_wg=csaw*(dbt-25)*u_wndw; shl_ww=ar_wwal*(dbt-25)*u_wall; shl_edr=csad*6.0*u_door; shl_ew=ar_ewal*6.0*u_wall; shl_par=2*ar_part*2*u_part; shl_roof=ar_roof*2*u_roof; shl_floor=shl_roof; shl_inf=19.8*(dbt-25)*inf_fac; if(doors==1) { inf_fac=8.1; }
else if(doors==2) { inf_fac=20.4; } else { inf_fac=8.4*doors; } shl_ppl=ppl*75; shl_eqp=power; shl=shl_wg+shl_ww+shl_edr+shl_ew+shl_par+shl_roof+shl_floor+shl_inf+shl_ppl+shl_e qp; lhl_inf=19.8*.006*50000; lhl_ppl=ppl*55; lhl=lhl_inf+lhl_ppl; thl=shl+lhl; tl=thl/3520; printf("\n\nThe Cooling Load Required for the given space is %f tonnes of refriferation(or T R )",tl); printf("\n\n\n"); } getch(); }
THERMAL CONDUCTIVITY OF MATERIALS- k - W/(m.K) Temperature - oC Material/Substance 25 Acetone
0.16
Acetylene (gas)
0.018
Acrylic
0.2
Air, athmosphere (gas)
0.024
Alcohol
0.17
Aluminum
250
Aluminum Oxide
30
Ammonia (gas)
0.022
Antimony
18.5
Argon (gas)
0.016
Asbestos-cement board
0.744
Asbestos-cement sheets
0.166
Asbestos-cement
2.07
Asbestos, loosely packed
0.15
125
225
255
250
Asbestos mill board
0.14
Asphalt
0.75
Balsa
0.048
Bitumen
0.17
Benzene
0.16
Beryllium
218
Blast furnace gas (gas)
0.02
Brass
109
Brick dense
1.31
Brick work
0.69
Cium
92
Carbon
1.7
Carbon dioxide (gas)
0.0146
Cement, portland
0.29
Cement, mortar
1.73
Chalk
0. 09
Chlorine (gas)
0.0081
Chrome Nickel Steel (18% Cr, 8 % Ni)
16.3
Clay, dry to moist
0.15 - 1.8
Clay, saturated
0.6 - 2.5
Cobalt
69
Concrete, light
0.42
Concrete, stone
1.7
Constantan
22
Copper
401
Corian (ceramic filled)
1.06
Corkboard
0.043
Cork, regranulated
0.044
Cork
0.07
Cotton
0.03
Carbon Steel
54
Cotton Wool insulation
0.029
Diatomaceous earth (Sil-ocel)
0.06
Earth, dry
1.5
Engine Oil
0.15
Ether
0.14
400
398
51
47
Ethylene (gas)
0.017
Epoxy
0.35
Ethylene glycol
0.25
Felt insulation
0.04
Fiberglass
0.04
Fiber insulating board
0.048
Fiber hardboard
0.2
Fireclay brick 500oC
1.4
Foam glass
0.045
Freon 12 (gas)
0.073
Freon (liquid)
0.07
Gasoline
0.15
Glass
1.05
Glass, Pearls, dry
0.18
Glass, Pearls, saturated
0.76
Glass, window
0.96
Glass, wool Insulation
0.04
Glycerol
0.28
Gold
310
Granite
1.7 - 4.0
Gravel
0.7
Gypsum or plaster board
0.17
Hairfelt
0.05
Hardboard high density
0.15
Hardwoods (oak, maple..)
0.16
Helium (gas)
0.142
Hydrochlor acid (gas)
0.013
Hydrogen (gas)
0.168
Hydrogen sulfide (gas)
0.013
Ice (0oC, 32oF)
2.18
Insulation materials
0.035 - 0.16
Iridium
147
Iron
80
Iron, wrought
59
Iron, cast
55
Kapok insulation
0.034
312
310
68
60
Kerosene
0.15
Krypton (gas)
0.0088
Lead Pb
35
Leather, dry
0.14
Limestone
1.26 - 1.33
Magnesia insulation (85%)
0.07
Magnesite
4.15
Magnesium
156
Marble
2.08 - 2.94
Mercury
8
Methane (gas)
0.030
Methanol
0.21
Mica
0.71
Mineral wool insulation materials, wool blankets ..
0.04
Molybdenum
138
Monel
26
Neon (gas)
0.046
Nickel
91
Nitrogen (gas)
0.024
Nylon 6
0.25
Oil, machine lubricating SAE 50
0.15
Olive oil
0.17
Oxygen (gas)
0.024
Paper
0.05
Paraffin Wax
0.25
Perlite, atmospheric pressure
0.031
Perlite, vacuum
0.00137
Plaster, gypsum
0.48
Plaster, metal lath
0.47
Plaster, wood lath
0.28
Plastics, foamed (insulation materials)
0.03
Platinum
70
Plywood
0.13
Polyethylene HD
0.42 - 0.51
Polypropylene
0.1 - 0.22
71
72
Polystyrene expanded
0.03
Polystyrol
0.043
Polyurethane foam
0.02
Porcelain
1.5
Propane (gas)
0.015
PTFE
0.25
PVC
0.19
Pyrex glass
1.005
Quartz mineral
3
Rock, solid
2-7
Rock, porous volcanic (Tuff)
0.5 - 2.5
Rock Wool insulation
0.045
Sand, dry
0.15 - 0.25
Sand, moist
0.25 - 2
Sand, saturated
2-4
Sandstone
1.7
Sawdust
0.08
Silica aerogel
0.02
Silicone oil
0.1
Silver
429
Snow (temp < 0oC)
0.05 - 0.25
Sodium
84
Softwoods (fir, pine ..)
0.12
Soil, with organic matter
0.15 - 2
Soil, saturated
0.6 - 4
Steel, Carbon 1%
43
Stainless Steel
16
Straw insulation
0.09
Styrofoam
0.033
Sulfur dioxide (gas)
0.0086
Tin Sn
67
Zinc Zn
116
Urethane foam
0.021
Vermiculite
0.058
Vinyl ester
0.25
Water
0.58
17
19
Water, vapor (steam)
0.016
Wood across the grain, white pine
0.12
Wood across the grain, balsa
0.055
Wood across the grain, yellow pine, timber
0.147
Wood, oak
0.17
Wool, felt
0.07
Xenon (gas)
0.0051
INDEX SR. NO. 1 2 3 4
CONTENT ACKNOWLEDGEMENT OBJECTIVE TERMINOLOGY SIZING THE SYSTEM
ACKNOWLEDGEMENT
This is to certify that we the team of four students namely Ramkaran khelwar(1208382), Virender kumar (1208415), Vipin chander (1208414) , Shashi kant (1208393) have worked under the able guidance of our mentor and tutor . We are constantly in their touch and received their help and . We heartly recognize and hail there help and without which it wouldn’t be a success.
OBJECTIVE The main aim of our project is:1. To estimate the cooling load for a multi floored building. 2. On the basis of the calculations made , to design a friendly method to find out the cooling load for any given space.
The analysis provides a procedure for preparing a manual calculation for cooling load. A number of published methods, tables and charts from industry handbooks, manufacturer’s engineering data and manufacturer’s catalog data usually provide a good source of design information and criteria in the preparation of the Cooling Load Calculation. It is not the intent of this course to duplicate this information but rather to extract appropriate data from these documents as well as provide a direction regarding the proper use or application of such data so that engineers and designers involved in preparing the calculations can make the appropriate decision and/or apply proper engineering judgment. The analysis includes two example calculations for better understanding and for the partial fulfillment of the subject.
TERMINOLOGY
Commonly used relative to heat transmission and load calculations are defined below in accordance with ASHRAE Standard , Refrigeration and Definitions. Space – is either a volume or a site without a partition or a partitioned room or group of rooms. Room – is an enclosed or partitioned space that is usually treated as single load. Zone – is a space or group of spaces within a building with heating and/or cooling requirements sufficiently similar so that comfort conditions can be maintained throughout by a single controlling device. Sensible Heat Gain – is the energy added to the space by conduction, convection and/or radiation. Latent Heat Gain – is the energy added to the space when moisture is added to the space by means of vapor emitted by the occupants, generated by a process or through air infiltration from outside or adjacent areas. Radiant Heat Gain – the rate at which heat absorbed is by the surfaces enclosing the space and the objects within the space. Space Heat Gain – is the rate at which heat enters into and/or is generated within the conditioned space during a given time interval. Space Cooling Load – is the rate at which energy must be removed from a space to maintain a constant space air temperature. Space Heat Extraction Rate - the rate at which heat is removed from the conditioned space and is equal to the space cooling load if the room temperature remains constant. Temperature, Dry Bulb – is the temperature of air indicated by a regular thermometer.
Temperature, Wet Bulb – is the temperature measured by a thermometer that has a bulb wrapped in wet cloth. The evaporation of water from the thermometer has a cooling effect, so the temperature indicated by the wet bulb thermometer is less than the temperature indicated by a dry-bulb (normal, unmodified) thermometer. The rate of evaporation from the wet-bulb thermometer depends on the humidity of the air. Evaporation is slower when the air is already full of water vapor. For this reason, the difference in the temperatures indicated by ordinary dry bulb and wet bulb thermometers gives a measure of atmospheric humidity. Temperature, Dewpoint – is the temperature to which air must be cooled in order to reach saturation or at which the condensation of water vapor in a space begins for a given state of humidity and pressure. Relative humidity - describes how far the air is from saturation. It is a useful term for expressing the amount of water vapor when discussing the amount and rate of evaporation. One way to approach saturation, a relative humidity of 100%, is to cool the air. It is therefore useful to know how much the air needs to be cooled to reach saturation. Thermal Transmittance or Heat Transfer Coefficient (U-factor) – is the rate of heat flow through a unit area of building envelope material or assembly, including its boundary films, per unit of temperature difference between the inside and outside air.
SIZING YOUR AIR-CONDITIONING SYSTEM
Concepts and fundamentals of air conditioner sizing is based on heat gain, and/or losses in a building. It is obvious that you will need to remove the amount of heat gain - if it is hot outside. Similarly, you'll need to add in the heat loss from your space - if outside temperature is cold. In short, heat gain and loss, must be equally balanced by heat removal, and addition, to get the desired room comfort that we want. The heat gain or heat loss through a building depends on: a. The temperature difference between outside temperature and our desired temperature. b. The type of construction and the amount of insulation is in your ceiling and walls. Let's say, that you have two identical buildings, one is build out of glass, and the other out of brick. Of course the one built with glass would require much more heat addition, or removal, compared to the other - given a same day. This is because the glass has a high thermal conductivity (U-value) as compared to the brick and also because it is transparent, it allows direct transmission of solar heat. c. How much shade is on your building’s windows, walls, and roof? Two identical buildings with different orientation with respect to the direction of sun rise and fall will also influence the air conditioner sizing. d. How large is your room? The surface area of the walls. The larger the surface area - the more heat can loose, or gain through it. e. How much air leaks into indoor space from the outside? Infiltration plays a part in determining our air conditioner sizing. Door gaps, cracked windows, chimneys - are the "doorways" for air to enter from outside, into your living space. f. The occupants. It takes a lot to cool a town hall full of people. g. Activities and other equipment within a building. Cooking? Hot bath? Gymnasium?
h. Amount of lighting in the room. High efficiency lighting fixtures generate less heat. i. How much heat the appliances generate. Number of power equipments such as oven, washing machine, computers, TV inside the space; all contribute to heat. The air conditioner's efficiency, performance, durability, and cost depend on matching its size to the above factors. Many designers use a simple square foot method for sizing the airconditioners. The most common rule of thumb is to use "1 ton for every 500 square feet of floor area". Such a method is useful in preliminary estimation of the equipment size. The main drawback of rules-of-thumb methods is the presumption that the building design will not make any difference. Thus the rules for a badly designed building are typically the same as for a good design. It is important to use the correct procedure for estimating heat gain or heat loss. Two groups— the Air Conditioning Contractors of America (ACCA) and the American Society of Heating, Refrigerating, and Air Conditioning Engineers (ASHRAE)—publish calculation procedures for sizing central air conditioners.
HEAT FLOW RATES
In air-conditioning design, four related heat flow rates, each of which varies with time, must be differentiated: a. Space heat gain ----------------How much heat (energy) is entering the space? b. Space cooling load -------------How much energy must be removed from the space to keep temperature and relative humidity constant? c. Space heat extraction-----------How much energy is the HVAC removing from the space? d. Cooling load (coil) ---------------How much energy is removed by the cooling coil serving various space plus any loads external to the spaces such as duct heat gain, duct leakage, fan heat and outdoor makeup air?
Space Heat Gain This instantaneous rate of heat gain is the rate at which heat enters into and/or is generated within a space at a given instant. Heat gain is classified by: The manner in which it enters the space – a. Solar radiation through transparent surfaces such as windows b. Heat conduction through exterior walls and roofs c. Heat conduction through interior partitions, ceilings and floors d. Heat generated within the space by occupants, lights, appliances, equipment and processes e. Loads as a result of ventilation and infiltration of outdoor air f. Other miscellaneous heat gains
Whether it is a sensible or latent gain -Sensible heat - Heat which a substance absorbs, and while its temperature goes up, the substance does not change state. Sensible heat gain is directly added to the conditioned space by conduction, convection, and/or radiation. Note that the sensible heat gain entering the conditioned space does not equal the sensible cooling load during the same time interval because of the stored heat in the building envelope. Only the convective heat becomes cooling load instantaneously. Sensible heat load is total of:a. Heat transmitted thru floors, ceilings, walls b. Occupant’s body heat c. Appliance & Light heat d. Solar Heat gain thru glass e. Infiltration of outside air f. Air introduced by Ventilation
Latent Heat Loads - Latent heat gain occurs when moisture is added to the space either from internal sources (e.g. vapor emitted by occupants and equipment) or from outdoor air as a result of infiltration or ventilation to maintain proper indoor air quality. Latent heat load is total of :a. Moisture-laden outside air form Infiltration & Ventilation b. Occupant Respiration & Activities c. Moisture from Equipment & Appliances
To maintain a constant humidity ratio, water vapor must condense on cooling apparatus at a rate equal to its rate of addition into the space. This process is called dehumidification and is very energy intensive, for instance, removing 1 kg of humidity requires approximately 0.7 kWh of energy. Space Heat Gain V/s Cooling Load (Heat Storage Effect)
Space Heat Gain is ≠ to Space Cooling Load The heat received from the heat sources (conduction, convection, solar radiation, lightning, people, equipment, etc.) does not go immediately to heating the room air. Only some portion of it is absorbed by the air in the conditioned space instantaneously leading to a minute change in its temperature. Most of the radiation heat especially from sun, lighting, people is first absorbed by the internal surfaces, which include ceiling, floor, internal walls, furniture etc. Due to the large but finite thermal capacity of the roof, floor, walls etc., their temperature increases slowly due to absorption of radiant heat. The radiant portion introduces a time lag and also a decrement factor depending upon the dynamic characteristics of the surfaces. Due to the time lag, the effect of radiation will be felt even when the source of radiation, in this case the sun is removed.
Differences between Space Heat Gain and Space Cooling Load Differences between instantaneous heat gain and cooling load is due to heat storage affect. The relation between heat gain and cooling load and the effect of the mass of the structure (light, medium & heavy) is shown below. From the figure it is evident that, there is a delay in the peak heat, especially for heavy construction.
DESIGN INFORMATION
To calculate the space cooling load, detailed building information, location, site and weather data, internal design information and operating schedules are required. Information regarding the outdoor design conditions and desired indoor conditions are the starting point for the load calculation and is discussed below. Outdoor Design Weather Conditions ASHRAE Handbook Fundamentals list tables of climate conditions : In these tables: The information provided in table 1a, 2a and 3a are for heating design conditions that include: a. Dry bulb temperatures corresponding to 99.6% and 99% annual cumulative frequency of occurrence b. Wind speeds corresponding to 1%, 2.5% and 5% annual cumulative frequency of occurrence, c. Wind direction most frequently occurring with 99.6% and 0.4% dry-bulb temperatures. d. Average of annual extreme maximum and minimum dry-bulb temperatures and standard deviations. The information provided in table 1b, 2b and 3b are for cooling and humidity control conditions that include: a. Dry bulb temperature corresponding to 0.4%, 1.0% and 2.0% annual cumulative frequency of occurrence and the mean coincident wet-bulb temperature (warm). These conditions appear in sets of dry bulb (DB) temperature and the mean coincident wet bulb (MWB) temperature since both values are needed to determine the sensible and latent (dehumidification) loads in the cooling mode.
b. Wet-bulb temperature corresponding to 0.4%, 1.0% and 2.0% annual cumulative frequency of occurrence and the mean coincident dry-bulb temperature c. Dew-point temperature corresponding to 0.4%, 1.0% and 2.0% annual cumulative frequency of occurrence and the mean coincident dry-bulb temperature and humidity ratio (calculated for the dew-point temperature at the standard atmospheric pressure at the elevation of the station). d. Mean daily range (DR) of the dry bulb temperature, which is the mean of the temperature difference between daily maximum and minimum temperatures for the warmest month (highest average dry-bulb temperature). These are used to correct CLTD values. In choosing the HVAC outdoor design conditions, it is neither economical nor practical to design equipment either for the annual hottest temperature or annual minimum temperature, since the peak or the lowest temperatures may occur only for a few hours over the span of several years. Economically speaking short duration peaks above the system capacity might be tolerated at significant reductions in first cost; this is a simple risk - benefit decision for each building design. Therefore, as a practice, the ‘design temperature and humidity’ conditions are based on frequency of occurrence. The summer design conditions have been presented for annual percentile values of 0.4, 1 and 2% and winter month conditions are based on annual percentiles of 99.6 and 99%. The term “design condition” refers to the %age of time in a year (8760 hours), the values of dry-bulb, dew-point and wet-bulb temperature exceed by the indicated percentage. The 0.4%, 1.0%, 2.0% and 5.0% values are exceeded on average by 35, 88, 175 and 438 hours. The 99% and 99.6% cold values are defined in the same way but are viewed as the values for which the corresponding weather element are less than the design condition 88 and 35 hours, respectively. 99.6% value suggests that the outdoor temperature is equal to or lower than design data 0.4% of the time.
Design condition is used to calculate maximum heat gain and maximum heat loss of the building. For comfort cooling, use of the 2.5% occurrence and for heating use of 99% values is recommended. The 2.5% design condition means that the outside summer temperature and coincident air moisture content will be exceeded only 2.5% of hours from June to September or 73 out of 2928 hours (of these summer months) i.e. 2.5% of the time in a year, the outdoor air temperature will be above the design condition.
BUILDING CHARACTERISTICS
To calculate space heat gain, the following information on building envelope is required: a. Architectural plans, sections and elevations – for estimating building dimensions/area/volume b. Building orientation (N, S, E, W, NE, SE, SW, NW, etc), location etc c. External/Internal shading, ground reflectance etc. d. Materials of construction for external walls, roofs, windows, doors, internal walls, partitions, ceiling, insulating materials and thick nesses, external wall and roof colors - select and/or compute U-values for walls, roof, windows, doors, partitions, etc. Check if the structure is insulated and/or exposed to high wind. e. Amount of glass, type and shading on windows
OPERATING SCHEDULES
Obtain the schedule of occupants, lighting, equipment, appliances, and processes that contribute to the internal loads and determine whether air conditioning equipment will be operated continuously or intermittently (such as, shut down during off periods, night setback, and weekend shutdown). Gather the following information: • Lighting requirements, types of lighting fixtures • Appliances requirements such as computers, printers, fax machines, water coolers, refrigerators, microwave, miscellaneous electrical s, cables etc • Heat released by the Cooling equipment. • Number of occupants, time of building occupancy and type of building occupancy
COOLING LOAD METHODOLOGY – CONSIDERATIONS & ASSUMPTIONS
Design cooling load takes into all the loads experienced by a building under a specific set of assumed conditions. The assumptions behind design cooling load are as follows: a. Weather conditions are selected from a long-term statistical database. The conditions will not necessary represent any actual year, but are representative of the location of the building. ASHRAE has tabulated such data. b. The solar loads on the building are assumed to be those that would occur on a clear day in the month chosen for the calculations. c. The building occupancy is assumed to be at full design capacity.
d. The ventilation rates are either assumed on air changes or based on maximum occupancy expected. e. All building equipment and appliances are considered to be operating at a reasonably representative capacity. f. Lights and appliances are assumed to be operating as expected for a typical day of design occupancy. g. Latent as well as sensible loads are considered. h. Heat flow is analyzed assuming dynamic conditions, which means that heat storage in building envelope and interior materials is considered. i. The latent heat gain is assumed to become cooling load instantly, whereas the sensible heat gain is partially delayed depending on the characteristics of the conditioned space. According to the ASHRAE regulations, the sensible heat gain from people is assumed 30% convection (instant cooling load) and 70% radiative (delayed portion). j. Peak load calculations evaluate the maximum load to size and select the refrigeration equipment. The energy analysis program compares the total energy use in a certain period with various alternatives in order to determine the optimum one. k. Space (zone) cooling load is used to calculate the supply volume flow rate and to determine the size of the air system, ducts, terminals, and diffs. The coil load is used to determine the size of the cooling coil and the refrigeration system. Space cooling load is a component of the cooling coil load. l. The heat transfer due to ventilation is not a load on the building but a load on the system.
CLTD/SCL/CLF METHOD OF LOAD CALCULATION (ASHRAE FUNDAMENTALS 1997)
As mentioned before, the heat gain to the building is not converted to cooling load instantaneously. CLTD (cooling load temperature difference), SCL (solar cooling load factor), and CLF (cooling load factor): all include the effect of (1) time-lag in conductive heat gain through opaque exterior surfaces and (2) time delay by thermal storage in converting radiant heat gain to cooling load. This approach allows cooling load to be calculated manually by use of simple multiplication factors. a. CLTD is a theoretical temperature difference that s for the combined effects of inside and outside air temp difference, daily temp range, solar raiation and heat storage in the construction assembly/building mass. It is affected by orientation, tilt, month, day, hour, latitude, etc. CLTD factors are used for adjustment to conductive heat gains from walls, roof, floor and glass. b. CLF s for the fact that all the radiant energy that enters the conditioned space at a particular time does not become a part of the cooling load instantly. The CLF values for various surfaces have been calculated as functions of solar time and orientation and are available in the form of tables in ASHRAE Handbooks. CLF factors are used for adjustm ent to heat gains from internal loads such as lights, occupancy, power appliances. c. SCL factors are used for adjustment to transmission heat gains from glass.
DIMENSIONS OF SPACE (LECTURE HALLS)
NO OF DOORS
:-
2
•
WIDTH
:-
0.95 m
•
LENGTH
:-
2.11 m
•
THICKNESS
:-
0.032 m
•
AREA
:-
2.0045 m^2
•
THERMAL CONDUCTIVITY
:-
.09 W/mK
NO. OF WINDOW
:-
3
•
WIDTH
:-
2.33 m
•
HEIGHT
:-
2.17 m
•
AREA
:-
5.0561 m^2
•
THICKNESS
:-
0.005 m
•
THERMAL CONDUCTIVITY (GLASS)
:-
.78 W/mk
PARTITION .33m (Brick thickness =0.28m
ROOM SPACE •
WIDTH
:-
8.10 m
•
LENGTH
:-
9.70 m
•
HEIGHT
:-
3.50 m
•
VOLUME OF SPACE
•
THICKNESS OF WALL
•
Plaster (Inside + Outside)
:-
0.05 m
•
Roof construction
:-
0.20 m (concrete)
•
THERMAL CONDUCTIVITY (CONCRETE) :-
.73W/mK
•
THERMAL CONDUCTIVITY (BRICK)
:-
1.32W/mK
•
THERMAL CONDUCTIVITY (PLASTER)
:-
.48W/mK
•
THERMAL CONDUCTIVITY (WOOD)
:-
.09W/mK
::-
274.995 m^3 .22m(east , west ; Brick thickness=0.20m)
FILM COEFFICIENT
F(o) F (i)
::-
23 W/m^2K 7 W/m^2K
INTERNAL LOAD FACTOR NO. OF TUBES
:-
6 ( 20 W EACH =120 WATT)
NO. OF FANS
:-
7 ( 40 W EACH =280 WATT)
TOTAL
:-
400 WATT
NO. OF OCCUPANTS
:-
61
CALCULATION FOR OVERALL THERMAL CO-EFFICENT FOR OUTSIDE AND INSIDE WALL WALL 1/U= 1/23 + .05/0.48 + 0.15/1.73 + 1/7 (OUTER FILM+ PLASTER+ BRICK+
INSIDE FILM)
U=2.47 W/m^2K
FOR PARTITION WALL 1/U = 1/7 + 0.05/0.48 + 0.28/1.32 + 1/7 (INSIDE + PLASTER + BRICK + INSIDE) U=1.66 W/m^2K
FOR ROOF AND FLOOR 1/U = 1/7 + 0.05/0.48 + 0.20/1.73 + 1/7 (INSIDE + PLASTER + CONCRETE + INSIDE) U=1.64W/m^2K
WINDOW GLASS 1/U = 1/23 + 0.005/0.78 + 1/7 U = 5.208
DOOR 1/U = 1/23 + 0.032/0.09 + 1/7 U=1.84
Area of East wall=31.88 m^2
Area of West wall=20.72 m^2
Area of partition =29.97 m^2
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 1) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST GLASS
15.17
232.92
---
3533.48
WEST WALL
20.72
18
2.47
921.21
EAST DOOR
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
NORTH WALL
29.97
12
2.47
888.31
FLOOR
98.57
2.5
1.64
404.14
PARTITION
29.97
0
1.66
0
ROOF
98.57
0
1.97
0
INFILTRATION 19.8cmm
18
20.4
7270
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = (18433.48 + 9240) W = 27673.86 W = 7.87 TR
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 2,3,4) ITEM
AREA(m^2)
WEST GLASS
15.17
∂T/∂ф/Sun Gain
FACTOR
232.92
---
W 3533.39
WEST WALL
20.72
18
2.47
921.21
EAST DOOR
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
FLOOR
98.57
2.5
1.64
404.14
PARTITION
29.97
0
1.66
0
PARTITION
29.97
0
1.66
0
ROOF
98.57
0
1.97
0
18
20.4
INFILTRATION 19.8cmm
7270
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = 3*(17545.46 + 9240) W = 3*26785.46 W = 80356.38 W = 22.85 TR
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 5) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST GLASS
15.17
232.92
---
3533.39
WEST WALL
20.72
18
2.47
921.21
EAST DOOR
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
FLOOR
98.57
2.5
1.64
404.14
PARTITION
29.97
0
1.66
0
PARTITION
29.97
8
1.66
398
ROOF
98.57
0
1.97
0
INFILTRATION 19.8cmm
18
20.4
7270
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = (17943.46 + 9240) W = 27183.46 W = 7.73TR
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 6,11) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST GLASS
15.17
232.92
---
3533.39
WEST WALL
20.72
18
2.47
921.21
EAST DOOR
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
NORTH WALL
29.97
12
2.47
888.31
FLOOR
98.57
0
1.64
0
0
1.66
PARTITION
29.97
0
ROOF
98.57
0
1.97
0
INFILTRATION 19.8cmm
18
20.4
7270
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = 2*(18029.37 + 9240) W = 2*27269.37 W = 54538.74 W = 15.51 TR
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 7,8,9,12,13,14) ITEM
AREA(m^2)
WEST GLASS
15.17
∂T/∂ф/Sun Gain
FACTOR
232.92
---
W 3111.49
WEST WALL
20.72
18
2.47
921.21
EAST DOOR
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
FLOOR
98.57
0
1.64
0
PARTITION
29.97
0
1.66
0
PARTITION
29.97
0
1.66
0
ROOF
98.57
0
1.97
0
18
20.4
7270
INFILTRATION 19.8cmm
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = 6*(17141.32 + 9240) W = 6*26381.32 W = 158287.92 W = 45.01 TR
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 10,15) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST GLASS
15.17
232.92
---
3533.40
WEST WALL
20.72
18
2.47
921.21
EAST DOOR
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
FLOOR
98.57
0
1.64
0
PARTITION
29.97
0
1.66
0
PARTITION
29.97
8
1.66
398
ROOF
98.57
0
1.97
0
18
20.4
7270
INFILTRATION 19.8cmm
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = 2*(17539.46 + 9240) W = 2*26779.46 W = 53558.92 W = 15.23 TR
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 16) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST GLASS
15.17
232.92
---
3533.49
WEST WALL
20.72
18
2.47
921.21
EAST DOOR
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
NORTH WALL
29.97
12
2.47
888.31
FLOOR
98.57
0
1.64
0
PARTITION
29.97
0
1.66
0
ROOF
98.57
18
1.97
3495.29
INFILTRATION 19.8cmm
18
20.4
7270
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = (21524.92 + 9240) W = 30764.92 W = 8.75 TR
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 17,18,19) ITEM
AREA(m^2)
WEST GLASS
15.17
∂T/∂ф/Sun Gain
FACTOR
232.92
---
W 3533.49
WEST WALL
20.72
18
2.47
921.21
EAST DOOR
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
FLOOR
98.57
0
1.64
0
PARTITION
29.97
0
1.66
0
PARTITION
29.97
0
1.66
0
ROOF
98.57
18
1.97
3495.29
INFILTRATION 19.8cmm
18
20.4
7270
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = 3*(20636.61 + 9240) W = 3*29876.61 W = 89629.83 W = 25.49 TR
LOAD CALCULATION (SENSIBLE HEAT) (Room No. 20) ITEM
AREA(m^2)
WEST GLASS
15.17
WEST WALL
20.72
EAST DOOR
∂T/∂ф/Sun Gain
FACTOR
232.92
W
---
3533.49
18
2.47
921.21
4.009
6
1.84
44.26
EAST WALL
31.88
6
2.47
472.46
FLOOR
98.57
0
1.64
0
PARTITION
29.97
0
1.66
0
PARTITION
29.97
8
1.66
398
ROOF
98.57
18
1.97
3495.29
INFILTRATION 19.8cmm
18
20.4
7270
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
60
75
4500
TUBES
6
20
120
FAN
7
40
280
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
60
_
55
3300
TOTAL LOAD TOTAL LOAD = SHL + LHL = (21034.61 + 9240) W = 30274.61 W = 8.61 TR
DIMENSIONS OF SPACE (TEACHERS’ ROOMS)
NO OF DOORS
:-
1
•
WIDTH
:-
0.95 m
•
LENGTH
:-
2.11 m
•
THICKNESS
:-
0.032 m
•
AREA
:-
2.0045 m^2
•
THERMAL CONDUCTIVITY
:-
.09 W/mK
NO. OF WINDOW
:-
1
•
WIDTH
:-
2.33 m
•
HEIGHT
:-
2.17 m
•
AREA
:-
5.0561 m^2
•
THICKNESS
:-
0.005 m
•
THERMAL CONDUCTIVITY (GLASS)
:-
.78 W/mk
PARTITION .33m (Brick thickness =0.28m)
ROOM SPACE •
WIDTH
:-
2.26 m
•
LENGTH
:-
2.4 m
•
HEIGHT
:-
3.50 m
•
VOLUME OF SPACE
:-
18.984 m^3
•
THICKNESS OF WALL
•
Plaster (Inside + Outside)
:-
0.05 m
•
Roof construction
:-
0.20 m (concrete)
•
THERMAL CONDUCTIVITY (CONCRETE) :-
.73W/mK
•
THERMAL CONDUCTIVITY (BRICK)
:-
1.32W/mK
•
THERMAL CONDUCTIVITY (PLASTER)
:-
.48W/mK
•
THERMAL CONDUCTIVITY (WOOD)
:-
.09W/mK
:-
.22m(east , west ; Brick thickness=0.20m)
FILM COEFFICIENT
F(o) F (i)
::-
23 W/m^2K 7 W/m^2K
INTERNAL LOAD FACTOR NO. OF TUBES
:-
1 ( 20 WATT )
NO. OF FANS
:-
1 ( 40 WATT )
TOTAL
:-
60 WATT
NO. OF OCCUPANTS
:-
2
Area of East/West Wall=7.91 m^2
Area of North/South Wall=3.3 m^2 / 8.4m^2
Area of partition =7.91 m^2
LOAD CALCULATION (SENSIBLE HEAT)
(Teachers’ Room 1,5,6,10)
ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST/EAST WALL 7.91
6
2.47
117.23
DOOR
0
1.84
0
12
2.47
888.31
1.64
22.22
2.004
NORTH/SOUTH WALL 29.97 FLOOR
5.42
2.5
PARTITION
7.91
0
1.66
0
ROOF
5.42
0
1.97
0
--
--
INFILTRATION 19.8cmm
2120
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
2
75
150
TUBES
1
20
20
FAN
1
40
40
EXTRA USAGE
--
--
300
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
2
_
55
110
TOTAL LOAD TOTAL LOAD = SHL + LHL = 4*(3657.76 + 6050) W = 4*9707.76 W = 38831.04 W = 11.04 TR
LOAD CALCULATION (SENSIBLE HEAT) (Teachers’ Room 2,3,4,7,8,9) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST/EAST WALL 7.91
0
2.47
0
DOOR
0
1.84
0
12
2.47
888.31
1.64
22.22
2.004
NORTH/SOUTH WALL 29.97 FLOOR
5.42
2.5
PARTITION
7.91
0
1.66
0
ROOF
5.42
0
1.97
0
--
--
INFILTRATION 19.8cmm
2120
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
2
75
150
TUBES
1
20
20
FAN
1
40
40
EXTRA USAGE
--
--
300
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
2
_
55
110
TOTAL LOAD TOTAL LOAD = SHL + LHL = 6*(3540.53 + 6050) W = 6*9590.53 W = 57543.18 W = 16.37 TR
LOAD CALCULATION (SENSIBLE HEAT) (Teachers’ Room 11,15,16,20,21,25,26,30) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST/EAST WALL 7.91
6
2.47
117.23
DOOR
0
1.84
0
NORTH/SOUTH WALL 29.97
12
2.47
888.31
FLOOR
5.42
0
1.64
0
PARTITION
7.91
0
1.66
0
ROOF
5.42
0
1.97
0
--
--
2.004
INFILTRATION 19.8cmm
2120
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
2
75
150
TUBES
1
20
20
FAN
1
40
40
EXTRA USAGE
--
--
300
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
2
_
55
110
TOTAL LOAD TOTAL LOAD = SHL + LHL = 8*(3635.54 + 6050) W = 8*9685.54 W = 76884.32 W = 21.87 TR
LOAD CALCULATION (SENSIBLE HEAT) (Teachers’ Room 12,13,14,17,18,19,22,23,24,27,28,29) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
WEST/EAST WALL 7.91
0
2.47
0
DOOR
0
1.84
0
NORTH/SOUTH WALL 29.97
12
2.47
888.31
FLOOR
5.42
0
1.64
0
PARTITION
7.91
0
1.66
0
ROOF
5.42
0
1.97
0
2.004
INFILTRATION 19.8cmm
--
--
2120
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
2
75
150
TUBES
1
20
20
FAN
1
40
40
EXTRA USAGE
--
--
300
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
2
_
55
110
TOTAL LOAD TOTAL LOAD = SHL + LHL = 12*(3518.31 + 6050) W = 12*9568.31 W = 113019.72 W = 32.14 TR
DIMENSIONS OF SPACE (H.O.D. ROOMS)
NO OF DOORS
:-
1
•
WIDTH
:-
0.95 m
•
LENGTH
:-
2.11 m
•
THICKNESS
:-
0.032 m
•
AREA
:-
2.0045 m^2
•
THERMAL CONDUCTIVITY
:-
.09 W/mK
PARTITION .33m (Brick thickness =0.28m)
ROOM SPACE •
WIDTH
:-
4.52 m
•
LENGTH
:-
2.4 m
•
HEIGHT
:-
3.50 m
•
VOLUME OF SPACE
:-
37.968 m^3
•
THICKNESS OF WALL
•
Plaster (Inside + Outside)
:-
0.05 m
•
Roof construction
:-
0.20 m (concrete)
:-
.22m(east , west ; Brick thickness=0.20m)
FILM COEFFICIENT
F(o) F (i)
::-
23 W/m^2K 7 W/m^2K
INTERNAL LOAD FACTOR NO. OF TUBES
:-
2 ( 20 WATT EACH, = 40W )
NO. OF FANS
:-
1 ( 40 WATT )
TOTAL
:-
80 WATT
NO. OF OCCUPANTS
:-
3
Area of East Wall=15.82 m^2
Area of North Wall=8.4m^2
Area of partition =15.82 m^2
Area of South Wall =6.4 m^2
Floor Area =10.85 m^2
LOAD CALCULATION (SENSIBLE HEAT) (H.O.D. Room, Ground Floor) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
EAST WALL
15.82
6
2.47
234.45
DOOR
2.004
6
1.84
22.12
NORTH WALL
8.4
18
2.47
373.46
10.85
2.5
1.64
44.5
6
1.66
157.56
0
1.97
FLOOR PARTITION ROOF
15.82 10.85
INFILTRATION 19.8cmm
--
--
SOUTH WALL
6
2.47
6.4
0 2120 94.85
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
3
75
225
TUBES
2
20
40
FAN
1
40
40
EXTRA USAGE
--
--
500
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
3
_
55
165
TOTAL LOAD TOTAL LOAD = SHL + LHL = (3851.94 + 6105) W = 9956.94 W = 2.83 TR
LOAD CALCULATION (SENSIBLE HEAT) (H.O.D. Room First Floor,Second Floor) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
EAST WALL
15.82
6
2.47
234.45
DOOR
2.004
6
1.84
22.12
NORTH WALL
8.4
18
2.47
373.46
10.85
0
1.64
0
6
1.66
157.56
0
1.97
FLOOR PARTITION ROOF
15.82 10.85
INFILTRATION 19.8cmm
--
--
SOUTH WALL
6
2.47
6.4
0 2120 94.85
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
3
75
225
TUBES
2
20
40
FAN
1
40
40
EXTRA USAGE
--
--
500
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
3
_
55
165
TOTAL LOAD TOTAL LOAD = SHL + LHL = 2*(3807.44 + 6105) W = 2*9912.44 W = 19824.88 W = 5.64 TR
LOAD CALCULATION (SENSIBLE HEAT) (H.O.D. Room Top Floor) ITEM
AREA(m^2)
∂T/∂ф/Sun Gain
FACTOR
W
EAST WALL
15.82
6
2.47
234.45
DOOR
2.004
6
1.84
22.12
NORTH WALL
8.4
18
2.47
373.46
10.85
0
1.64
0
6
1.66
157.56
18
1.97
384.74
FLOOR PARTITION ROOF
15.82 10.85
INFILTRATION 19.8cmm
--
--
SOUTH WALL
6
2.47
6.4
2120 94.85
INTERNAL SENSIBLE HEAT GAIN SOURCE
QUANTITY
CAPACITY
TOTAL LOAD
PEOPLE
3
75
225
TUBES
2
20
40
FAN
1
40
40
EXTRA USAGE
--
--
500
LATENT HEAT
SOURCE
QUANTITY
HUMIDITY
FACTOR
W
INFILTRATION
19.8cmm
.006
50000
5940
PEOPLE
3
_
55
165
TOTAL LOAD TOTAL LOAD = SHL + LHL = (4192.18 + 6105) W = 10297.18 W = 2.93 TR
PROGRAM FILE FOR THE FRIENDLY SOFTWARE FOR FINDING OUT THE COOLING LOAD OF ANY GIVEN SPACE OF KNOWN DATA
#include<stdio.h> #include
int doors,tubes,ppl=60,fans,wndws; clrscr(); printf("\n\n\t\tCOOLING LOAD ESTIMATION FOR A SINGLE ROOM"); printf("\t\n\nEnter the outside dry bulb temprature in degree celsius:"); scanf("%f",&dbt); printf("\t\n\nEnter the outside wet bulb temprature in degree celsius:"); scanf("%f",&wbt);
if(wbt>dbt) { printf("\n\n\tDry bulb temp. can never be less than Wet bulb temp."); } else { printf("\n\nThe inside comfort conditions being used are ::\n\n\tInner Dry Bulb Temprature(in degree C) = 25\n\n\tRelative Humidity = 50 %"); printf("\n\nThe capacity of the room is taken as 60"); printf("\n\nEnter the details of the Room::"); printf("\n\n\No. of Doors::"); scanf("%d",&doors); printf("\n\nWidth, Height and Thickness of door(m) ::"); scanf("%f%f%f",&wd,&hd,&td); csad=wd*hd*doors; printf("\n\nThe total door area(sq. m) is :: %f",csad); printf("\n\n\tREFER TO APPENDIX 1 FOR THERMAL CONDUCTIVITY OF MATERIALS"); printf("\n\nEnter the thermal conductivity of door material(W/mK) ::"); scanf("%f",&th_cn_d); printf("\n\nNo. of Windows :: ");
scanf("%d",&wndws); printf("\n\nWidth, Height and Thickness of glass used in windows(m) :: "); scanf("%f%f%f",&ww,&hw,&tw); csaw=ww*hw*wndws; printf("\n\nThe total cross sectional area of the windows(sq. m) is %f",csaw); printf("\n\nEnter the thermal conductivity of glass used for windows(W/mK) ::"); scanf("%f",&th_cn_g); printf("\n\nEnter the dimensions of the room space(in m) :: "); printf("\n\nWidth, Length and Height :: "); scanf("%f%f%f",&wrs,&lrs,&hrs); volr=wrs*lrs*hrs; ar_roof=wrs*lrs; csa_wal=lrs*hrs; printf("\n\nThe volume of the room(cu. m) is %f",volr); printf("\n\nEnter the total thickness of brick material in the wall(m) ::"); scanf("%f",&tbw); printf("\n\nEnter the thermal conductivity of brick material used(W/mK) ::"); scanf("%f",&th_cn_b); printf("\n\nEnter the thickness of plaster being used(m) ::"); scanf("%f",tpw);
printf("\n\nEnter the thermal conductivity of plaster used in the wall(W/mK) ::"); scanf("%f",&th_cn_p); printf("\n\nEnter the total thickness of concrete material used in the roof(m) ::"); scanf("%f",&tcr); printf("\n\nEnter the thermal conductivity of the concrete material used(W/mK) ::"); scanf("%f",&th_cn_c); tpr=tpw; tppw=tpw; printf("\n\nEnter the total thickness of brick material in the partition wall(m) ::"); scanf("%f",tbpw); printf("\n\nNo. of 20W tubelights used in the room ::"); scanf("%f",tubes); printf("\n\nNo. of 40W fans used in the room ::"); scanf("%d",fans); printf("\n\nThe Total Wattage of all the other equipments used in the room ::"); scanf("%f",&watt); power=(20.0*tubes)+(40.0*fans)+watt;
u_wall=1.0/((1.0/23.0)+(tpw/th_cn_p)+(tbw/th_cn_b)+(1.0/7.0)); u_part=1.0/((2.0/7.0)+(tppw/th_cn_p)+(tbpw/th_cn_b)); u_roof=1.0/((2.0/7.0)+(tpr/th_cn_p)+(tcr/th_cn_c)); u_floor=u_roof; u_wndw=1.0/((1.0/23.0)+(1.0/7.0)+(tw/th_cn_g)); u_door=1.0/((1.0/23.0)+(1.0/7.0)+(td/th_cn_d)); ar_ewal=csa_wal-csad; ar_wwal=csa_wal-csaw; ar_part=wrs*hrs; shl_wg=csaw*(dbt-25)*u_wndw; shl_ww=ar_wwal*(dbt-25)*u_wall; shl_edr=csad*6.0*u_door; shl_ew=ar_ewal*6.0*u_wall; shl_par=2*ar_part*2*u_part; shl_roof=ar_roof*2*u_roof; shl_floor=shl_roof; shl_inf=19.8*(dbt-25)*inf_fac; if(doors==1) { inf_fac=8.1; }
else if(doors==2) { inf_fac=20.4; } else { inf_fac=8.4*doors; } shl_ppl=ppl*75; shl_eqp=power; shl=shl_wg+shl_ww+shl_edr+shl_ew+shl_par+shl_roof+shl_floor+shl_inf+shl_ppl+shl_e qp; lhl_inf=19.8*.006*50000; lhl_ppl=ppl*55; lhl=lhl_inf+lhl_ppl; thl=shl+lhl; tl=thl/3520; printf("\n\nThe Cooling Load Required for the given space is %f tonnes of refriferation(or T R )",tl); printf("\n\n\n"); } getch(); }
THERMAL CONDUCTIVITY OF MATERIALS- k - W/(m.K) Temperature - oC Material/Substance 25 Acetone
0.16
Acetylene (gas)
0.018
Acrylic
0.2
Air, athmosphere (gas)
0.024
Alcohol
0.17
Aluminum
250
Aluminum Oxide
30
Ammonia (gas)
0.022
Antimony
18.5
Argon (gas)
0.016
Asbestos-cement board
0.744
Asbestos-cement sheets
0.166
Asbestos-cement
2.07
Asbestos, loosely packed
0.15
125
225
255
250
Asbestos mill board
0.14
Asphalt
0.75
Balsa
0.048
Bitumen
0.17
Benzene
0.16
Beryllium
218
Blast furnace gas (gas)
0.02
Brass
109
Brick dense
1.31
Brick work
0.69
Cium
92
Carbon
1.7
Carbon dioxide (gas)
0.0146
Cement, portland
0.29
Cement, mortar
1.73
Chalk
0. 09
Chlorine (gas)
0.0081
Chrome Nickel Steel (18% Cr, 8 % Ni)
16.3
Clay, dry to moist
0.15 - 1.8
Clay, saturated
0.6 - 2.5
Cobalt
69
Concrete, light
0.42
Concrete, stone
1.7
Constantan
22
Copper
401
Corian (ceramic filled)
1.06
Corkboard
0.043
Cork, regranulated
0.044
Cork
0.07
Cotton
0.03
Carbon Steel
54
Cotton Wool insulation
0.029
Diatomaceous earth (Sil-ocel)
0.06
Earth, dry
1.5
Engine Oil
0.15
Ether
0.14
400
398
51
47
Ethylene (gas)
0.017
Epoxy
0.35
Ethylene glycol
0.25
Felt insulation
0.04
Fiberglass
0.04
Fiber insulating board
0.048
Fiber hardboard
0.2
Fireclay brick 500oC
1.4
Foam glass
0.045
Freon 12 (gas)
0.073
Freon (liquid)
0.07
Gasoline
0.15
Glass
1.05
Glass, Pearls, dry
0.18
Glass, Pearls, saturated
0.76
Glass, window
0.96
Glass, wool Insulation
0.04
Glycerol
0.28
Gold
310
Granite
1.7 - 4.0
Gravel
0.7
Gypsum or plaster board
0.17
Hairfelt
0.05
Hardboard high density
0.15
Hardwoods (oak, maple..)
0.16
Helium (gas)
0.142
Hydrochlor acid (gas)
0.013
Hydrogen (gas)
0.168
Hydrogen sulfide (gas)
0.013
Ice (0oC, 32oF)
2.18
Insulation materials
0.035 - 0.16
Iridium
147
Iron
80
Iron, wrought
59
Iron, cast
55
Kapok insulation
0.034
312
310
68
60
Kerosene
0.15
Krypton (gas)
0.0088
Lead Pb
35
Leather, dry
0.14
Limestone
1.26 - 1.33
Magnesia insulation (85%)
0.07
Magnesite
4.15
Magnesium
156
Marble
2.08 - 2.94
Mercury
8
Methane (gas)
0.030
Methanol
0.21
Mica
0.71
Mineral wool insulation materials, wool blankets ..
0.04
Molybdenum
138
Monel
26
Neon (gas)
0.046
Nickel
91
Nitrogen (gas)
0.024
Nylon 6
0.25
Oil, machine lubricating SAE 50
0.15
Olive oil
0.17
Oxygen (gas)
0.024
Paper
0.05
Paraffin Wax
0.25
Perlite, atmospheric pressure
0.031
Perlite, vacuum
0.00137
Plaster, gypsum
0.48
Plaster, metal lath
0.47
Plaster, wood lath
0.28
Plastics, foamed (insulation materials)
0.03
Platinum
70
Plywood
0.13
Polyethylene HD
0.42 - 0.51
Polypropylene
0.1 - 0.22
71
72
Polystyrene expanded
0.03
Polystyrol
0.043
Polyurethane foam
0.02
Porcelain
1.5
Propane (gas)
0.015
PTFE
0.25
PVC
0.19
Pyrex glass
1.005
Quartz mineral
3
Rock, solid
2-7
Rock, porous volcanic (Tuff)
0.5 - 2.5
Rock Wool insulation
0.045
Sand, dry
0.15 - 0.25
Sand, moist
0.25 - 2
Sand, saturated
2-4
Sandstone
1.7
Sawdust
0.08
Silica aerogel
0.02
Silicone oil
0.1
Silver
429
Snow (temp < 0oC)
0.05 - 0.25
Sodium
84
Softwoods (fir, pine ..)
0.12
Soil, with organic matter
0.15 - 2
Soil, saturated
0.6 - 4
Steel, Carbon 1%
43
Stainless Steel
16
Straw insulation
0.09
Styrofoam
0.033
Sulfur dioxide (gas)
0.0086
Tin Sn
67
Zinc Zn
116
Urethane foam
0.021
Vermiculite
0.058
Vinyl ester
0.25
Water
0.58
17
19
Water, vapor (steam)
0.016
Wood across the grain, white pine
0.12
Wood across the grain, balsa
0.055
Wood across the grain, yellow pine, timber
0.147
Wood, oak
0.17
Wool, felt
0.07
Xenon (gas)
0.0051
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