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Engineering Design - Radiant Cooling

General Evaluation       Control of Airborne Nosocomial Infections       Design Examples

      Step 1       Step 2       Step 3       Step 4       Step 5


Select link below for catalog version.
Radiant Cooling (307 kb - PDF)


GENERAL EVALUATION

     Radiant cooling system, like radiant heating, obeys the same physical laws of radiant energy
transfer. The difference is that when a space is radiantly cooled, the radiant surface is lowered
to a temperature below that of other surfaces in the room. The radiant ceiling is absorbing radiant
energy from surroundings and occupants that are warmer than the ceiling. The radiant cooling system
is to other air-water system in the arrangements of the system components. Room thermal conditions
are maintained primarily by direct transfer of radiant energy, rather than by convection cooling.
Water circulating through the radiant panels can provide all the heating and most of the sensible
cooling. Air supplied to the space provides ventilation and dehumidification.

      The air handling equipment will be appreciably smaller than if an air cooling system were used alone,
because the radiant cooling system will remove a very high percentage of the sensible heat from a
space. The air flow into a space can, be substantially lower than if the building were entirely air
cooled, thus greatly reducing cold drafts which lead to discomfort. People under a cooled
radiant ceiling radiate energy to the ceiling, losing heat in a more comfortable manner than
blowing cold air across them.

The radiant ceiling will carry away, by conduction and convection, a considerable percentage of
the electric light heat load.

Principal advantages of radiant cooling systems are:

1.) Comfort levels are better than other conditioning systems because radiant loads are treated
      directly and air circulation in a space is at normal ventilation levels.

2.) No mechanical equipment is required on the outside walls improving the wall and floor space.

3.) All pumps, fans, and filters are centrally located, simplifying maintenance and operation.

4.) No space requirement in the mechanical equipment room. This feature is especially important
      in applications where space is at a premium, where cleanliness is essential, or where
      dictated by legal requirements (hospital patient rooms).

5.) Cooling and heating can be simultaneous, without central zone control or seasonal changeover,
      when four-pipe systems are used.

6.) Supply air quantities usually do not exceed those required for ventilation and dehumidification.

7.) Draperies and curtains can be installed at the outside wall without interfering with the
      cooling system.

8.) The modular panel provides flexibility to meet changes in partitioning.

9.) The 100% outdoor air system may be installed with less severe penalties in terms
      of refrigeration load because of reduced air quantities.

10.) A common central air system can serve both the inferior perimeter zones.

11.) Wet surface cooling coils are eliminated from the occupied space, reducing the
      potential for septic contamination.

12.) The panel system can use the automatic sprinkler system piping.

13.) Radiant cooling and minimum supply air quantities provide a draft-free environment.

14.) Noise associated with fan coil or induction units is eliminated.

     Radiant cooling systems are similar to other air-water systems in the arrangement
of the system components. Room thermal conditions are maintained primarily by direct
transfer of radiant energy, rather than by convection cooling. The room cooling loads are
calculated in the convectional manner. Manufacturer’s ratings generally are for total
performance and can be applied directly to the room load. The amount of energy required to
remove heat hydronically is approximately ten percent less than required with an air system.
Also, design temperatures can be as much as five to six degrees higher for cooling than with a
convective system due to the system uniformly controlling the rate of energy transfer among
objects within the space.


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CONTROL OF AIRBORNE NOSOCOMIAL INFECTIONS

     Airborne nosocomial infections is the spreading of infectious bacteria and fungi which develops
in re-circulated air systems nooks and crannies and is redistributed into hospital rooms. Many
infections and even deaths have been traced to fungi and other micro-organisms which find an ideal
breeding place in patient-room units. Hospital design has been influenced by many recent developments
which focus on the necessity for basing selection of hospital mechanical equipment on the physical
well-being of the patient and the economic well-being of the hospital. The cooling source for a
radiant panel cooling system is completely concealed in the ceiling plenum. Since there is no
mechanical equipment associated with a radiant panel cooling system in the patient room, there are no
areas to support the growth of bacteria and fungi and no nooks and crannies in the system components
to collect dust and lint which intensify respiratory problems.

     A radiant panel cooling system supplies most of the cooling requirements through the radiant energy
transfer process. This reduces the air requirements to only the amount of air needed for proper ventilation
and relative humidity control, which is so small it’s economically feasible to completely eliminate re-circulated
air. This will permit the use of 100% outside air to be adequately filtered and conditioned to safeguard
against infiltration of bacteria. This is the main reason why a radiant panel cooling system is the most
technologically advanced approach to providing an environment to control airborne nosocomial infection.


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DESIGN PROCEDURE


     The use of radiant panel cooling systems to remove sensible heat from a space will reduce
the quantity of air supplied to the room. The air supply system will primarily serve to provide
adequate moisture control, odor control and a constant air supply. The minimum amount of air supplied
for good ventilation should be based on local codes if required or a minimum recommended air supply
quantity of 0.4 CFM per square foot of conditioned area. The design of a radiant panel cooling system
follows the normal design procedure used for an air-water system.


The following items must be taken into consideration when designing a radiant panel cooling system;

1.) Must determine the rooms design dry bulb temperature, relative humidity, and dew point.

2.) Calculate the sensible heat gain and the latent heat gain to the room.

3.) Select the mean water temperature (MWT).

4.) Determine the panel performance from the performance curves.

5.) Determine the panel area available in the room and total panel pick-up.

6.) Determine the minimum air quantity to offset the latent heat gain and in accordance with
     good ventilation practices and local codes.

7.) Determine the design panel area and design air quantity.

8.) Determine the water quantity and pressure drop.


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     The following section will demonstrate by an example step-by-step procedure for designing a
radiant panel cooling system.


Example
Design Criteria Used


Outside Design Conditions : Summer - 95 degrees F dry bulb, 78 degrees F wet bulb
Winter - -15 degrees F dry bulb

Inside Design Conditions : 76 degrees F dry bulb, 45% relative humidity,
53 degrees F dew point, 60 gr/lb of moisture

Primary Chilled Water Temperature : 40 - 45 degrees F

Calculated Internal Sensible Load (room facing South) : Summer - 5,500 btu/hr/gain
Winter - 7,000 btu/hr/loss

Calculated Internal Latent Load People, infiltration, etc. : Summer - 510 btu/hr/gain

Total Floor Area of Space : 130 square foot room width 12 feet.



Step 1 :

     Determine Air Supply Conditions. Air quantity must meet minimum code requirements and be sufficient
for comfort and odor removal. Air must handle all of latent load. For comfort not less than
.4 cfm / sq. ft. of floor space is recommended.

1.) Code requires two air changes (a.c.) / hr of outside air be supplied to room and
ten a.c. / hr be exhausted from toilet.

Supply Air cfm = 130 sq ft x 9 ft ceiling x 2 a.c. = 40 cfm
60 min / hr

Total exhaust = 6' x 8' x 8' x 10 a.c. = 64 cfm
60 min / hr

Soiled Linen Cabinet exhaust = 15 cfm
TOTAL EXHAUST = 79 cfm

2. ) For air motion, use : .6 cfm / sq ft

130 sq ft x .6 cfm / sq ft = 78 cfm
( Note : from 1.) and 2.) above, select minimum air of 80 cfm)

3. ) Check latent capacity. Calculate the internal moisture pickup with 80 cfm.

Internal Latent Load = Internal moisture pickup CFM conditioned x 0.68

0.68 = 1,060 x 60
7,000 x 13.34

1060 btu = Heat of Vaporization
60 = Minutes per hour
7000 = Grains per pound
15.34 = Cu/ft/ lb of Std air

510 btu / hr = 9.5 grains / lb.
80 cfm x 0.68

Use 10 grains / lb.
Determine the required delivered air condition to offset this 10 grain/lb. pickup.
Grains maintained - grains pickup = grains to delivered

60 grains / lb - 10 grains / lb = 50 grains / lb (maximum in delivered air )

     Refer to Pyschrometric Chart attached. Air entering air handling unit in summer 95 degree F
dry bulb, 78 degree F wet bulb, 118 gr/lb at point "A" cooling and dehumidifying occurs along
line "A" - "B" and leaves coil at 52 degrees F dry bulb, 50 degrees F wet bulb, 50 gr / lb
as required. Fan "C" which is delivered air to room . "D" represents design room conditions.

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Step 2 :

     Determine panel capacity. The secondary chilled water temperature supply to the ceiling should be at
or above the design dew point of the room. Use one degree F higher as design. Room dew point of
53 degree F + 1 = 54 degrees F supply water temperature.

     Determine Mean Water Temperature (MWT) for use with performance curves. Use five degrees F water
temperature rise W.T.R.

MWT = Supply water temperature + 1/2 design WTR
MWT = 54 degrees + 2.5 degrees = 56.5 degrees

Refer to Sun-El Cooling Performance Curve.

( Room Air Temp - MWT ) = 76 degrees F dry bulb - 56 degrees F
= 19.5 degrees F difference.

Using 19.5 degrees F difference find intersection with Cooling curve follow horizontally to left
to find performance of 49 btu/hr/sq ft of Radiant Ceiling.

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Step 3 :

     Determine Panel Area required for Cooling. Take advantage of cooling by air
and determine this quantify.

Room Supply Sensible
Conditioned cfm x 1.08 x Air - Air = cooling
Temp Temp with air

1.08 = 60 x 0.24 60 = Minutes per hour
13.34 0.24 = Specific heat of air
13.34 = Cu. Ft. / lb. of standard air

80 cfm x 1.08 x ( 76 - 54 ) = 1900 btu / hr

Subtract this from total room sensible to determine load to be done by panel.
( 5,500 btu / hr - 1,900 btu / hr ) = 3,600 btu / hr
Divide this quantity by performance, as determined in Step 2 to find area of radiant panel required.

3,600 btu /hr = 74 sq. ft required
49 btu / hr / sq ft of panel

If we use a 2'x4' Sun-El ELF radiant panel this would be 8 sq. ft / panel and ten panels would be
required. Remainder of ceiling would be filled out with a matching steel acoustical panel.

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Step 4 :

     Check Heating Performance to determine if this amount of panel is sufficient for heating requirements.
The calculated heat loss is 7,000 btu / hr. Add to this any heating required for the delivered air.

     Normally the air is reset in winter to a few degrees below room temperature, but not above room
temperature (unless for special circumstances). Let's assume air is reset to 70 degrees F, therefore,
we must add this load to the panel output needed.

Room Supply
cfin x 1.08 x Air - Air = btu / hr
Temp Temp to be added

80 x 1.08 x (76 - 70 ) = 520 btu / hr add to room load
7,000 btu / hr + 520 btu / hr = 7,520 btu / hr

     Divide this by the 74 sq. ft of panels to determine output and check this on the Sun-el panel heating
performance curve.      7,520 btu / hr = 102 btu / sq. ft of panel
74 sq. ft

     Enter curve at right at 102 btu / hr and follow horizontally to intersection with Sun-el heating
and cooling curve, follow vertically down to find a MWT of 142 degrees F is required. If the hot
water design is based on 20 degree water temperature drop (WTD) add one half of this to MWT to
determine supply temperature water 142 degrees + 10 degrees = 152 degrees supply water will
handle design load.

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Step 5 :

     Determine gallons per minute and water pressure drop for ceiling area. Refer to Pressure Drop
Curve for design pressure drop on heating and cooling.

GPM = Total btu / hr / for panels
500 x Water Temperature Difference

500 = 8.34 x 60
8.34 = Pounds per gallon
60 = Minutes per hour

Cooling : GPM = 3600 btu / hr
500 x 5 degrees

GPM = 1.44 GPM

     Enter the Water Pressure Drop Curve for Extruded Aluminum Panels at 1.5 GPM go vertically up to
intersect the curve line, follow horizontally to the left to determine the value of Head Loss,
Ft / 100 ft. tube, read the value of four head loss in ft. of water / 100ft. tube. The head
loss for this room would be calculated as follows :

Linear Foot of Panel x Number of Tubes = Linear Foot of Head Drop

Linear Foot of Head Drop = Multiplier
100 Foot of Tube

160 L ft. = 1.6 as Multiplier
100

Multiplier x 4 head loss in ft. of Water / 100 ft. tube = Total Pressure Drop

1.6 x 4 = 6.4 Ft. Total Pressure Drop

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Cooling Performance Curve


Heating Performance Curve With Cooling Application


Psychrometric Chart


 
 

 

 

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