CA1082935A - Heating and cooling system and method - Google Patents
Heating and cooling system and methodInfo
- Publication number
- CA1082935A CA1082935A CA304,485A CA304485A CA1082935A CA 1082935 A CA1082935 A CA 1082935A CA 304485 A CA304485 A CA 304485A CA 1082935 A CA1082935 A CA 1082935A
- Authority
- CA
- Canada
- Prior art keywords
- volume
- coil
- gas
- ambient
- condenser
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
Abstract
HEATING AND COOLING SYSTEM AND METHOD
Abstract of the Disclosure A vapor compression heating/cooling system and method of operation having improved Coefficient of Performance and Capacity. Post-condenser liquid is cooled in a subcooler coil by a stream of air. One embodiment provides a warming machine or heat pump in which the condenser coil is within a volume to be warm and the evaporator coil is on the outside exposed to ambient air. A stream of ambient air is pumped in heat exchange relationship with the subcooler coil to recover and expel heat from the coil into the volume. Where the volume comprises the interior of a house or other building structure the stream of air from the subcooler creates an over pressure within the volume to minimize infiltration of ambient air. In another embodiment the system is employed for refrigerating a volume such as a reefer trailer or other mobile compartment. The evaporator coil is within the com-partment and the condenser coil is outside the compartment exposed to ambient air. A stream of air from the compartment is directed by a duct in heat exchange relationship with the subcooler coil and thence to ambient for expelling heat from the post-condenser liquid.
Abstract of the Disclosure A vapor compression heating/cooling system and method of operation having improved Coefficient of Performance and Capacity. Post-condenser liquid is cooled in a subcooler coil by a stream of air. One embodiment provides a warming machine or heat pump in which the condenser coil is within a volume to be warm and the evaporator coil is on the outside exposed to ambient air. A stream of ambient air is pumped in heat exchange relationship with the subcooler coil to recover and expel heat from the coil into the volume. Where the volume comprises the interior of a house or other building structure the stream of air from the subcooler creates an over pressure within the volume to minimize infiltration of ambient air. In another embodiment the system is employed for refrigerating a volume such as a reefer trailer or other mobile compartment. The evaporator coil is within the com-partment and the condenser coil is outside the compartment exposed to ambient air. A stream of air from the compartment is directed by a duct in heat exchange relationship with the subcooler coil and thence to ambient for expelling heat from the post-condenser liquid.
Description
Background of the Invèntion ~`
This invention relates in general to vapor compression .
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'~`, ' , , ` ` , -~ heating and refrigerating systems. In particular the invention relates to heat pumps and refrigerating machines -for respectively heating or cooling a volume.
A major element of lost work in vapor compression , 5 machines such as heat pumps and air conditioners is the loss due to throttling the condenser liquid to the evaporator.
The Coefficient of Performance (COPH) of such a system is in accordance with the equation:
COPH = (hb - he)/(hC hb) where hc = enthalpy of superheated vapor after compression and hb = enthalpy of vapor after heated in evaporator and entering the compressor and he = enthalpy of condensed liquid after cooling in ;, condenser From the formula it is seen that the COPH is increased :.
for either a warming or cooling machine by extracting heat ,, from the condensed liquid. Where subcooling of post-condenser liquid is accomplished without affecting compression work then there is a gain in useful heating or cooling effect with a resulting increase in COPH and Capacity.
The described low temperature heating acquisition is even more beneficial to COPH than would be the effect of reversably expanding the liquid and applying the expansion work to reduce the net compression work~ An example would be a heat pump evaporating at 5F and condensing at 100F
with a compression efficiency of 55~ and condenser subcooled - to 85F resulting in a COPH of about 3.2. A reversible liquid expander from 85F to 15F would ret~rn about 5% of the compression gross work and increase the COPH to about 3.45, while subcooling from ~5F to 15F usefully would !
, -2-'~' -` ~08Z935 increase the Capacity about 19.4% and raise the COPH to about 3.85. A problem which exlsts in applying these concepts to heat pump systems is that of providing a useful heating load of below 70F.
In houses and other building structures a major component of heat loss amounting to about 20~ to 40% comprises infiltration of the heating load from ambient. This results when the inside air of about 70F is replaced with cold ambient air . which leaks into the structure as the air is driven by stack - 10 effect and wind.
Objects and Summary of the Invention It is a general object of the invention to provide a ~-vapor compression heating/cooling system and method of -operation having increased COPH and Capacity.
Another object is to provide a system and method of the , type described in which post-condenser liquid is cooled for ', increasing COPH and Capacity.
Another object is to provide a system of the type described incorporating a warming machine or heat pump in which ambient air is employed for subcooling the post-condenser liquid with the heated air then being introducedinto the volume being warmed.
Another object is to provide a heat pump system for a home or other inhabited enclosure in which ambient air is pumped in heat exchange relationship with a subcooler coil and into the enclosure to create an over pressure which minimizes infiltration by ambient air.
Another object is to provide a system of the type described for refrigerating an enclosure in which cold air within the enclosure is directed in heat exchange lV82g35 .
relationship with a subcooler coil for extracting heat and expelling the heat to ambient.
; The invention in summary comprises a system and method of operation of a refrigerating or warming machine in which heat is respectfully extracted from or introduced into a , volume. A working fluid is compressed and then condensed by ambient air for the refrigerating machine or with gas within the volume for the warming machine. Post-condenser liquid is then subcooled with gas from the volume for the refrigerating machine or with ambient air for the warming machine. The subcooled liquid is expanded for cooling gas in the volume ,.
,.
for the refrigerating machine or the expanded gas is heated ' with ambient air for the heating machine. In the heat pump embodiment for heating a house a stream of ambient air for subcooling the liquid is pumped into the house to create an . , , over pressure for minimizing infiltration of outside air.
In the embodiment for refrigerating a mobile compartment a duct directs inside air for subcooling in a path which exits from the enclosure in a direction counter the direction of movement to assist in withdrawing the subcooling gas.
The foregoing and additional objects and features of the invention will appear from the following description in , which the several embodiments had been set forth in detail , in connection with the accompanying drawings.
Brief Description of the Drawings ~, Figure 1 is a schematic drawing of a warming machine ' embodiment of the invention shown in use as a heat pump for a house.
Figure 2 is a schematic diagram of the refrigerating machine embodiment of the invention shown in use with a . .
:
~0~93s ` reefer trailer.
Description Of The Preferred Embodiments In the drawings Figure 1 illustrates generally at 10 a warming machine embodiment of the invention comprising a heat pump for heating the inside volume of a house 12. The heat pump comprises a vapor compression machine including a ;~ compressor 14 which compresses a suitable working vapor such as R22 refrigerant, a trademark for the flourinated hy-drocarbon having the formula CHClF2. The compressed vapor is directed into condenser coil 16 mounted in a housing 18 within the volume 20 to be warmed. A blower 22 pumps inside air into the housing in heat exchange relationship with coil 16 for cooling the vapor into a liquid. The air is heated by the coil and directed through outlet 24 into the volume.
; 15 Post-condenser liquid is directed into a subcooler coil . .
26 within housing 28. A blower 30 pumps ambient air through , the inlet of the housing and in heat exchange relationship with the subcooler coil. The stream of air extracts heat from the post-condenser liquid and is directed through housing outlet 32 into the volume to be warmed. A control , valve 34 is employed in the outlet for controlling the rate ' of subcooling air flow. The controi valve can be manually , set, or it could comprise a suitable thermostatic damper of ; 1 the type conventionally used in refrigerator-freezers.
Either type of damper would be ad]usted to maintain a predetermined exit temperature of the subcooler air stream.
The ambient air pumped by blower 30 through the subcooler creates an over pressure within volume 20 relative to ,~ ambient air pressure. This over pressure serves to minimize ,~, 30 infiltration or leakage of cold ambient air through the , -5-i :
10~3293S
house structure. The over pressure level required would depend upon various factors including the extent of leakage openings in the structure and the wind velocity encountered '~ at any particular time. Preferably the overpressure within the volume is at a level which is approximately equal to the ~ windward side air pressure.
; The blower 30 could also be eliminated by connecting a duct, not shown, between subcooling housing outlet 32 and the inlet of condenser blower 22 so that a single stream of ambient air is pumped by blower 22 through both the subcooler and condenser housings.
Liquid refrigerant from the subcooler coil is expanded through a throttling valve 34 into evaporator coil 36.
Ambient air circulates in heat exchange relationship with the evaporator coil for transferring heat to the refrigerant.
The rate of flow through the throttling valve is controlled by a suitable flow control of the sub-cooling type having a bulb 38 mounted on the condenser exit.
An example of the use and operation of the embodiment Of Figure 1 is as follows. Subcooler 26 comprises an air-cooled liquid heat exchanger formed of a helical coil of bristle-fin tubing having approximately 50 square feet of air side surface for use with a nominal two ton heat pump.
; Blower 30 is rated at 50 cfm capacity.
During operation the vapor from compressor 14 is condensed into a liquid in coil 16 with the heat of condensation transferred to the air stream pumped by blower 22 through , ; housing 18 and into the volume to be warmed. The post-condenser liquid is cooled in coil 26 by ambient air pumped by blower 30 into housing with 28 heat extracted from the lV82935 liquid being carried by the air stream into the house. The liquid from the subcooler coil is expanded through throttling valve 34 into evaporator coil 36 where the relatively colder vapor is warmed by ambient air. Damper 34 is adjusted in accordance with outside wind conditions to deliver warmed ambient air from the outlet of the subcooler housing at a temperature or. the order of 70F. The over pressure within volume 20 created by pumping of the warmed ambient air resists infiltration of ambLent air through the building structure. Increasing wind conditions will result in a requirement of increase air flow through the subcooler with a resulting drop in temperature of that air flow; however, ~ .
- the subcooling heat is fully utilized in suppressing in-filtration loss when there is any windward side inflow.
; 15 With inflow stopped the effectiveness of the subcooling heat is in the ratio of:
; K = (70- TSupply)/(70 ~ Tambient) , It will be noted that the added subcooling heat is obtained at no energy cost into the system. Moreover, the ; 20 equipment cost is relatively modest in that only a small subcooler heat exchanger, housing, damper and the optional blower, are provided. The subcooling heat will exceed approximately 20% of the base heat pump capacity on very cold days, and to a lesser percentage on milder days. The effectiveness of the subcooling heat is highest on windy ~:~ days when added capacity is most needed.
~ Figure 2 illustrates another embodiment of the invention f ~ for use in refrigerating a volume. In this embodiment the refrigerated volume 40 comprises a mobile compartment, illustrated as a reefer trailer 41.
:
lU8Zg35 A vapor compression refrigerating machine 42 is provided on the trailer. The machine includes a compressor 44 which compresses a working fluid such as R22 refrigerant into a condenser coil 46 mounted within a housing 48 on the trailer roof. The housing is provided with inlet and outlet openings through which a stream of ambient air is directed during relative movement of the trailer. The ambient air cools the compressed vapor which is then directed into a subcooler coil 50 mounted in a duct 52 within the trailer volume. An inlet portion 54 of the duct concentrates a stream of escaping cold air from the trailer into heat exchange relationship with the subcooler coil. An outlet portion 56 of the duct projects through the trailer roof and discharges the air stream in a direction counter the direction of trailer movement. Forward movement of the trailer thereby ; creates a partial vacuum at the outlet to assist in drawing air through the duct.
Liquid from the subcooler is expanded through a throttling valve 58. Flow through the throttling valve is controlled by suitable means such as a sub-cooling type control having a bulb 60 mounted on the condenser exit. Vapor expands from valve 58 into an evaporator coil 62 mounted in a housing 64 within the trailer. A blower 66 pumps inside trailer air ;' into the evaporator housing where it is cooled and then directed through outlet 68 back to the trailer volume.
In the use and operation of the embodiment of Figure 2 the COPH and Capacity of the refrigerating machine is increased through subcooling of the post-condenser liquid by cold air from the trailer which otherwise would leak out due to the pressure of infiltrating air caused by motion of the .. _ ~ _ ' .
-' ~08Z935 i trailer. In other words heat is extracted from the post- -condenser liquid by causing a concentrated flow of escaping cold air (which is thereby warm), the cooling effect of which would otherwise be lost due to such infiltration.
While the foregoing embodiments are presently considered to be preferred it is understood that numerous variations and modifications may be made therein by those skilled in the art and it is intended to cover in the appended claims all such variations and modifications as fall within the true spirit and scope of the invention.
.
:.
., ?
.
_g_
This invention relates in general to vapor compression .
.
"
.. . . ..
,, i ,. . ~ . , , ~. . . . . .
, . :.;
. . .
,, :.. . :.
'' `' ;-''" ~ , .. , '' '' . . S
.~ . ,, ~ I
~.Y,~ i .
~ ~ . ~ ' ~ I ' " ~
` .
. . ` .
'~`, ' , , ` ` , -~ heating and refrigerating systems. In particular the invention relates to heat pumps and refrigerating machines -for respectively heating or cooling a volume.
A major element of lost work in vapor compression , 5 machines such as heat pumps and air conditioners is the loss due to throttling the condenser liquid to the evaporator.
The Coefficient of Performance (COPH) of such a system is in accordance with the equation:
COPH = (hb - he)/(hC hb) where hc = enthalpy of superheated vapor after compression and hb = enthalpy of vapor after heated in evaporator and entering the compressor and he = enthalpy of condensed liquid after cooling in ;, condenser From the formula it is seen that the COPH is increased :.
for either a warming or cooling machine by extracting heat ,, from the condensed liquid. Where subcooling of post-condenser liquid is accomplished without affecting compression work then there is a gain in useful heating or cooling effect with a resulting increase in COPH and Capacity.
The described low temperature heating acquisition is even more beneficial to COPH than would be the effect of reversably expanding the liquid and applying the expansion work to reduce the net compression work~ An example would be a heat pump evaporating at 5F and condensing at 100F
with a compression efficiency of 55~ and condenser subcooled - to 85F resulting in a COPH of about 3.2. A reversible liquid expander from 85F to 15F would ret~rn about 5% of the compression gross work and increase the COPH to about 3.45, while subcooling from ~5F to 15F usefully would !
, -2-'~' -` ~08Z935 increase the Capacity about 19.4% and raise the COPH to about 3.85. A problem which exlsts in applying these concepts to heat pump systems is that of providing a useful heating load of below 70F.
In houses and other building structures a major component of heat loss amounting to about 20~ to 40% comprises infiltration of the heating load from ambient. This results when the inside air of about 70F is replaced with cold ambient air . which leaks into the structure as the air is driven by stack - 10 effect and wind.
Objects and Summary of the Invention It is a general object of the invention to provide a ~-vapor compression heating/cooling system and method of -operation having increased COPH and Capacity.
Another object is to provide a system and method of the , type described in which post-condenser liquid is cooled for ', increasing COPH and Capacity.
Another object is to provide a system of the type described incorporating a warming machine or heat pump in which ambient air is employed for subcooling the post-condenser liquid with the heated air then being introducedinto the volume being warmed.
Another object is to provide a heat pump system for a home or other inhabited enclosure in which ambient air is pumped in heat exchange relationship with a subcooler coil and into the enclosure to create an over pressure which minimizes infiltration by ambient air.
Another object is to provide a system of the type described for refrigerating an enclosure in which cold air within the enclosure is directed in heat exchange lV82g35 .
relationship with a subcooler coil for extracting heat and expelling the heat to ambient.
; The invention in summary comprises a system and method of operation of a refrigerating or warming machine in which heat is respectfully extracted from or introduced into a , volume. A working fluid is compressed and then condensed by ambient air for the refrigerating machine or with gas within the volume for the warming machine. Post-condenser liquid is then subcooled with gas from the volume for the refrigerating machine or with ambient air for the warming machine. The subcooled liquid is expanded for cooling gas in the volume ,.
,.
for the refrigerating machine or the expanded gas is heated ' with ambient air for the heating machine. In the heat pump embodiment for heating a house a stream of ambient air for subcooling the liquid is pumped into the house to create an . , , over pressure for minimizing infiltration of outside air.
In the embodiment for refrigerating a mobile compartment a duct directs inside air for subcooling in a path which exits from the enclosure in a direction counter the direction of movement to assist in withdrawing the subcooling gas.
The foregoing and additional objects and features of the invention will appear from the following description in , which the several embodiments had been set forth in detail , in connection with the accompanying drawings.
Brief Description of the Drawings ~, Figure 1 is a schematic drawing of a warming machine ' embodiment of the invention shown in use as a heat pump for a house.
Figure 2 is a schematic diagram of the refrigerating machine embodiment of the invention shown in use with a . .
:
~0~93s ` reefer trailer.
Description Of The Preferred Embodiments In the drawings Figure 1 illustrates generally at 10 a warming machine embodiment of the invention comprising a heat pump for heating the inside volume of a house 12. The heat pump comprises a vapor compression machine including a ;~ compressor 14 which compresses a suitable working vapor such as R22 refrigerant, a trademark for the flourinated hy-drocarbon having the formula CHClF2. The compressed vapor is directed into condenser coil 16 mounted in a housing 18 within the volume 20 to be warmed. A blower 22 pumps inside air into the housing in heat exchange relationship with coil 16 for cooling the vapor into a liquid. The air is heated by the coil and directed through outlet 24 into the volume.
; 15 Post-condenser liquid is directed into a subcooler coil . .
26 within housing 28. A blower 30 pumps ambient air through , the inlet of the housing and in heat exchange relationship with the subcooler coil. The stream of air extracts heat from the post-condenser liquid and is directed through housing outlet 32 into the volume to be warmed. A control , valve 34 is employed in the outlet for controlling the rate ' of subcooling air flow. The controi valve can be manually , set, or it could comprise a suitable thermostatic damper of ; 1 the type conventionally used in refrigerator-freezers.
Either type of damper would be ad]usted to maintain a predetermined exit temperature of the subcooler air stream.
The ambient air pumped by blower 30 through the subcooler creates an over pressure within volume 20 relative to ,~ ambient air pressure. This over pressure serves to minimize ,~, 30 infiltration or leakage of cold ambient air through the , -5-i :
10~3293S
house structure. The over pressure level required would depend upon various factors including the extent of leakage openings in the structure and the wind velocity encountered '~ at any particular time. Preferably the overpressure within the volume is at a level which is approximately equal to the ~ windward side air pressure.
; The blower 30 could also be eliminated by connecting a duct, not shown, between subcooling housing outlet 32 and the inlet of condenser blower 22 so that a single stream of ambient air is pumped by blower 22 through both the subcooler and condenser housings.
Liquid refrigerant from the subcooler coil is expanded through a throttling valve 34 into evaporator coil 36.
Ambient air circulates in heat exchange relationship with the evaporator coil for transferring heat to the refrigerant.
The rate of flow through the throttling valve is controlled by a suitable flow control of the sub-cooling type having a bulb 38 mounted on the condenser exit.
An example of the use and operation of the embodiment Of Figure 1 is as follows. Subcooler 26 comprises an air-cooled liquid heat exchanger formed of a helical coil of bristle-fin tubing having approximately 50 square feet of air side surface for use with a nominal two ton heat pump.
; Blower 30 is rated at 50 cfm capacity.
During operation the vapor from compressor 14 is condensed into a liquid in coil 16 with the heat of condensation transferred to the air stream pumped by blower 22 through , ; housing 18 and into the volume to be warmed. The post-condenser liquid is cooled in coil 26 by ambient air pumped by blower 30 into housing with 28 heat extracted from the lV82935 liquid being carried by the air stream into the house. The liquid from the subcooler coil is expanded through throttling valve 34 into evaporator coil 36 where the relatively colder vapor is warmed by ambient air. Damper 34 is adjusted in accordance with outside wind conditions to deliver warmed ambient air from the outlet of the subcooler housing at a temperature or. the order of 70F. The over pressure within volume 20 created by pumping of the warmed ambient air resists infiltration of ambLent air through the building structure. Increasing wind conditions will result in a requirement of increase air flow through the subcooler with a resulting drop in temperature of that air flow; however, ~ .
- the subcooling heat is fully utilized in suppressing in-filtration loss when there is any windward side inflow.
; 15 With inflow stopped the effectiveness of the subcooling heat is in the ratio of:
; K = (70- TSupply)/(70 ~ Tambient) , It will be noted that the added subcooling heat is obtained at no energy cost into the system. Moreover, the ; 20 equipment cost is relatively modest in that only a small subcooler heat exchanger, housing, damper and the optional blower, are provided. The subcooling heat will exceed approximately 20% of the base heat pump capacity on very cold days, and to a lesser percentage on milder days. The effectiveness of the subcooling heat is highest on windy ~:~ days when added capacity is most needed.
~ Figure 2 illustrates another embodiment of the invention f ~ for use in refrigerating a volume. In this embodiment the refrigerated volume 40 comprises a mobile compartment, illustrated as a reefer trailer 41.
:
lU8Zg35 A vapor compression refrigerating machine 42 is provided on the trailer. The machine includes a compressor 44 which compresses a working fluid such as R22 refrigerant into a condenser coil 46 mounted within a housing 48 on the trailer roof. The housing is provided with inlet and outlet openings through which a stream of ambient air is directed during relative movement of the trailer. The ambient air cools the compressed vapor which is then directed into a subcooler coil 50 mounted in a duct 52 within the trailer volume. An inlet portion 54 of the duct concentrates a stream of escaping cold air from the trailer into heat exchange relationship with the subcooler coil. An outlet portion 56 of the duct projects through the trailer roof and discharges the air stream in a direction counter the direction of trailer movement. Forward movement of the trailer thereby ; creates a partial vacuum at the outlet to assist in drawing air through the duct.
Liquid from the subcooler is expanded through a throttling valve 58. Flow through the throttling valve is controlled by suitable means such as a sub-cooling type control having a bulb 60 mounted on the condenser exit. Vapor expands from valve 58 into an evaporator coil 62 mounted in a housing 64 within the trailer. A blower 66 pumps inside trailer air ;' into the evaporator housing where it is cooled and then directed through outlet 68 back to the trailer volume.
In the use and operation of the embodiment of Figure 2 the COPH and Capacity of the refrigerating machine is increased through subcooling of the post-condenser liquid by cold air from the trailer which otherwise would leak out due to the pressure of infiltrating air caused by motion of the .. _ ~ _ ' .
-' ~08Z935 i trailer. In other words heat is extracted from the post- -condenser liquid by causing a concentrated flow of escaping cold air (which is thereby warm), the cooling effect of which would otherwise be lost due to such infiltration.
While the foregoing embodiments are presently considered to be preferred it is understood that numerous variations and modifications may be made therein by those skilled in the art and it is intended to cover in the appended claims all such variations and modifications as fall within the true spirit and scope of the invention.
.
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Claims (14)
1. A method of operating a refrigerating or warming machine in which heat is extracted or introduced, respectively, from or into a volume, including the steps of compressing a working fluid, condensing the compressed fluid into a liquid by transferring heat from the fluid to ambient gas for the refrigerating machine or to gas within the volume for the warming machine, subcooling the liquid with a stream of gas directed from the volume to ambient for the refrigerating machine or from ambient into the volume for the warming machine, reducing the pressure of the subcooled liquid to cause it to expand into a gas while undergoing a reduction in temperature, and transferring heat from the gas in the volume to the expanded gas for the refrigerating machine or transferring heat from ambient gas to the expanded gas for the heating machine.
2, A method as in Claim 1 in which the warming machine comprises a heat pump which includes a condenser coil within the volume for condensing the compressed fluid, an evaporator coil outside the volume for heating the expanded gas, and a subcooler coil connected in series between the condenser and evaporator coils, the step of subcooling the liquid including pumping a stream of gas from ambient in heat exchange relationship with the subcooler coil and thereafter into the volume whereby heat is recovered from the liquid in the subcooler coil and introduced into the volume for increasing the Coefficient of Performance and Capacity of the heat pump.
3. A method as in Claim 2 in which the ambient gas is pumped into the volume to raise the pressure therein to a level which reduces infiltration of ambient gas into the volume.
4. A method as in Claim 3 which the volume is defined by an enclosure forming a house or other structure for inhabitation, and the ambient gas is pumped into the en-closure to create overpressure therein at a level which minimizes infiltration of ambient air due to outside wind and/or stack effect.
5. A method as in Claim 1 in which the refrigerating machine includes a condenser coil outside the volume, an evaporator coil within the volume and a subcooler coil connected in series between the condenser coil and evaporator coil, and gas is extracted from the volume along a path in heat exchange relationship with the sub cooler coil and thereafter to ambient whereby heat extracted from the condensed liquid in the subcooler coil is expelled to ambient for increasing the Coefficient of Performance and Capacity of the refrigerating machine.
6. A method as in Claim 5 in which the refrigerating machine includes a mobile refrigerating compartment, the compressed fluid is condensed by directing a stream of relative moving ambient air in heat exchange relationship with the condenser coil during movement of the compartment, and creating a partial vacuum by movement of the compartment relative to ambient for extracting gas within the compartment along said path in heat exchange relationship with the subcooler coil.
7. A system for heating or cooling gas within a volume, the system having means for compressing a working fluid, means for condensing the compressed fluid to a liquid, and means for evaporating the liquid, said condenser means being in heat exchange relationship with ambient gas and said evaporator means being in heat exchange relationship with gas in the volume for cooling the latter, or said condenser means being in heat exchange relationship with gas in the volume and said evaporator means being in heat exchange relationship with ambient gas for heating gas in the volume, and means for subcooling post-condenser liquid for increasing the Coefficient of Performance and Capacity of the system, said post-condenser liquid being subcooled by gas within the volume which is thereafter directed to ambient where the volume is to be cooled, or the post-condenser liquid is subcooled by ambient gas which is directed into the volume where the latter is to be heated.
8. A system as in Claim 7 for heating gas within a volume defined by an enclosure, said condensing means includes a condenser coil within the enclosure, said evap-orating means includes an evaporator coil in heat exchange relationship with ambient, and the subcooling means includes a subcooler coil within the enclosure and connected in series between the condenser coil and evaporator means.
9. A system as in Claim 8 in which the subcooling means includes means for pumping ambient air along a path into the enclosure in heat exchange relationship with the subcooler coil.
10. A system as in Claim 9 in which the pumping means pumps ambient air into the enclosure to create a pressure therein relative to ambient pressure for minimizing in filtration of ambient air into the enclosure.
11. A system as in Claim 10 in which the enclosure com-prises a house or other structure for inhabitation, and the overpressure in the house or structure is at a level to resist infiltration of ambient air due to wind.
12. A system as in Claim 7 for cooling gas within a volume defined by an enclosure in which the condensing means comprises a condenser coil in heat exchange relationship with ambient gas, the evaporating means includes an evap-orator coil within the enclosure, and the subcooling means includes a subcooler coil within the enclosure and connected in series between the condenser and evaporator coils.
13. A system as in Claim 12 in which the enclosure comprises a mobile compartment together with means forming a passage for concentrating and directing gas within the compartment along a stream in heat exchange relationship with the subcooling coil and out of the compartment.
14. A system as in Claim 13 in which the passage means includes a duct having an inlet portion within the enclosure disposed about the subcooler coil and an outlet portion extending out of the enclosure with its open end facing in a direction counter to the direction of movement of the com-partment whereby relative movement of the compartment creates a reduction in pressure within the duct for drawing gas along said stream through the duct.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US83228377A | 1977-09-12 | 1977-09-12 | |
| US832,283 | 1977-09-12 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1082935A true CA1082935A (en) | 1980-08-05 |
Family
ID=25261221
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA304,485A Expired CA1082935A (en) | 1977-09-12 | 1978-05-31 | Heating and cooling system and method |
Country Status (8)
| Country | Link |
|---|---|
| JP (1) | JPS5444339A (en) |
| CA (1) | CA1082935A (en) |
| DE (1) | DE2822965A1 (en) |
| DK (1) | DK238678A (en) |
| FR (1) | FR2402845A1 (en) |
| GB (1) | GB1587709A (en) |
| NO (1) | NO145853C (en) |
| SE (1) | SE7806199L (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| IT1192407B (en) * | 1982-04-22 | 1988-04-13 | S I E T T E Soc Impianti Elett | HEAT PUMP SYSTEM FOR AIR CONDITIONING OF RAILWAY CARRIAGES FOR PASSENGERS |
| US4683726A (en) * | 1986-07-16 | 1987-08-04 | Rejs Co., Inc. | Refrigeration apparatus |
| JP5183521B2 (en) * | 2009-02-12 | 2013-04-17 | 能美防災株式会社 | Sprinkler fire extinguishing equipment and sprinkler head used in this sprinkler fire extinguishing equipment |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2100867A (en) * | 1936-07-31 | 1937-11-30 | Gen Electric | Air conditioning system |
| US2474304A (en) * | 1946-01-28 | 1949-06-28 | Drayer Hanson | Reversible cycle heat pump |
| FR1023656A (en) * | 1950-08-22 | 1953-03-23 | Arrangement of the condenser circuits of the refrigerating machines for the use of the heat released | |
| FR1032737A (en) * | 1951-01-19 | 1953-07-03 | Ruhrstahl Ag | Refrigeration machine powered by compressed air, for cooling air used for ventilation of mines |
| US2841963A (en) * | 1956-10-18 | 1958-07-08 | Gen Motors Corp | Refrigerating apparatus |
| GB942688A (en) * | 1961-06-22 | 1963-11-27 | Bfrtram Robert Leigh | Improvements relating to space and water heating systems |
| JPS5129170Y2 (en) * | 1971-04-30 | 1976-07-22 | ||
| US3783629A (en) * | 1972-09-13 | 1974-01-08 | C Phillips | Refrigeration system |
| FR2256381A1 (en) * | 1973-12-27 | 1975-07-25 | Tour Agenturer Ab | Arrangement for heating or cooling a flow medium - part of air currents diverted to a circuit containing e.g. ammonia in a heat exchanger |
| FR2282606A1 (en) * | 1974-08-22 | 1976-03-19 | Rellier Eugene | Building heating and cooling system - extracts heat from removed air by refrigeration fluid and transfers to air delivered to rooms |
| SE396126B (en) * | 1975-02-18 | 1977-09-05 | Projectus Ind Produkter Ab | PROCEDURE AND DEVICE FOR TEMPERATING A SEVERAL PREMISES WITH INBOARD DIFFERENT AND VARIING HEATING NEEDS |
| FR2323963A1 (en) * | 1975-09-11 | 1977-04-08 | Rellier Eugene | Heat pump for air conditioning - uses baffles to selectively circulate air through set of heat exchangers |
-
1978
- 1978-05-17 GB GB20103/78A patent/GB1587709A/en not_active Expired
- 1978-05-26 DE DE19782822965 patent/DE2822965A1/en not_active Withdrawn
- 1978-05-30 DK DK238678A patent/DK238678A/en unknown
- 1978-05-30 JP JP6486778A patent/JPS5444339A/en active Granted
- 1978-05-30 SE SE7806199A patent/SE7806199L/en unknown
- 1978-05-31 CA CA304,485A patent/CA1082935A/en not_active Expired
- 1978-05-31 NO NO781899A patent/NO145853C/en unknown
- 1978-05-31 FR FR7816238A patent/FR2402845A1/en not_active Withdrawn
Also Published As
| Publication number | Publication date |
|---|---|
| DE2822965A1 (en) | 1979-03-15 |
| GB1587709A (en) | 1981-04-08 |
| SE7806199L (en) | 1979-03-13 |
| FR2402845A1 (en) | 1979-04-06 |
| DK238678A (en) | 1979-03-13 |
| NO145853C (en) | 1982-06-09 |
| JPS5444339A (en) | 1979-04-07 |
| NO781899L (en) | 1979-03-13 |
| NO145853B (en) | 1982-03-01 |
| JPS5517305B2 (en) | 1980-05-10 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |