EP0058259A1 - Energy conserving heat exchange apparatus for refrigerating machines, and refrigerating machine equipped therewith - Google Patents
Energy conserving heat exchange apparatus for refrigerating machines, and refrigerating machine equipped therewith Download PDFInfo
- Publication number
- EP0058259A1 EP0058259A1 EP81300602A EP81300602A EP0058259A1 EP 0058259 A1 EP0058259 A1 EP 0058259A1 EP 81300602 A EP81300602 A EP 81300602A EP 81300602 A EP81300602 A EP 81300602A EP 0058259 A1 EP0058259 A1 EP 0058259A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- water
- refrigerant
- exchanger
- refrigerating machine
- heat
- 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.)
- Granted
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 90
- 239000003507 refrigerant Substances 0.000 claims abstract description 42
- 238000005057 refrigeration Methods 0.000 claims abstract description 18
- 239000000498 cooling water Substances 0.000 claims 1
- 239000008236 heating water Substances 0.000 abstract 1
- 238000010438 heat treatment Methods 0.000 description 5
- 239000012530 fluid Substances 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 238000004134 energy conservation Methods 0.000 description 2
- 239000011159 matrix material Substances 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D17/00—Domestic hot-water supply systems
- F24D17/02—Domestic hot-water supply systems using heat pumps
-
- 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
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
-
- 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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/04—Desuperheaters
Definitions
- the present invention relates generally to refrigerating machines, and more particularly to a commercial cube/ crushed ice-making machine.
- the control system is responsive to a refrigerant pressure in the condenser so as to maintain it at an optimum efficiency for the refrigeration system, as well as to the output water temperature from the condenser.
- a refrigerator or ice-making machine has a closed loop refrigeration system including in series therein: a compressor, a refrigerant-to-water condenser whereby heat rejected from the closed loop system is transferred to the heat reclamation means through the condenser, an expansion valve, and an evaporator.
- the machine includes a control system having means responsive to both a refrigerant pressure in the condenser and a water temperature in the condenser for controlling heat exchanging water flow through the condenser while maintaining a pre-determined refrigerant pressure therein.
- an ice-maker and heat reclamation system constructed in accordance with the present invention, and generally indicated at 10, includes a commercial ice-maker 11 such as sold under the trademark ROSS-TEMP, and an indirect heat reclamation device which is a refrigerant-to-water condenser 12 which is conventional in itself and which, in this embodiment, is positioned externally of the ice-maker.
- the condenser 12 is preferably connected to a conventional external-water supply which, in this embodiment, is shown to include a water pump 13 and a hot water storage tank 14 connected in series with the coolant side of the condenser 12.
- any commercial ice-maker may be utilized in the system of the present invention
- two commercial ice-making systems are ideally suited for use with the heat reclamation system of the present invention.
- a layer of ice is formed on the bottom of a working sheet or plate.
- the second type of commercial ice-maker utilizes a hollow cylinder with ice being formed on an exterior surface thereof.
- An auger or the like is sleeved over the evaporator and includes a helical working edge which sweeps across the hollow cylindrical surface to shave ice therefrom in order to create "crushed" ice.
- the refrigeration system of the ice-maker 11 includes a conventional refrigerant compressor 15 having a high pressure exhaust port 15a which is connected by conduit 16a to refrigerant inlet port 12a of the heat reclamation condenser 12.
- the refrigerant cutlet port 12b is connected by conduit 16b to a secondary air-cooled condenser 17 having a cooling fan 18 and a fan control switch 18a associated therewith.
- a refrigerant receiver or accumulator 19 is operatively positioned between the secondary condenser and a thermal expansion valve 20 by conduits 16c and 16d.
- a conventional evaporator 21 and conduit 16e are downstream of the valve and operatively connected via conduit 16f to a low pressure inlet port 15b of the compressor.
- the air-cooled secondary condenser 17 may be the original equipment condenser for the separate ice-maker. If the refrigerant-to-water condenser 12 is mounted within the physical confines of the ice-maker 11, it is understood that it-could be sized to completely replace the secondary air-cooled condenser 11. The purpose of the secondary condenser will be discussed in connection with the operation of the system.
- the water supply includes a pump 13 which receives water from an inlet conduit 22 and pumps same through outlet conduit 23 to the water inlet port 12c of the refrigerant-to-water condenser 12 where the water is positioned in heat exchange relation with the high pressure refrigerant and passes out water outlet port 12d, through temperature actuated sensor 30, and conduit 24 to the hot water storage tank 14 where the water may be discharged through conduit 25.
- a pump 13 which receives water from an inlet conduit 22 and pumps same through outlet conduit 23 to the water inlet port 12c of the refrigerant-to-water condenser 12 where the water is positioned in heat exchange relation with the high pressure refrigerant and passes out water outlet port 12d, through temperature actuated sensor 30, and conduit 24 to the hot water storage tank 14 where the water may be discharged through conduit 25.
- the condenser 12 may act as a primary or secondary heating source for the water supply.
- the control system does not provide for operation of the compressor if the ice machine is filled to capacity, it is assumed that in most installations the condenser 12 will act as only a secondary heat source for the water supply.
- the flow of water from pump 13 into the refrigerant-to-water condenser 12 is regulated by a valve 26 which acts in response to the pressure of the refrigerant at outlet 12b of the condenser.
- the operational pressure of the refrigerant proximately ranges from about 100 psig to about 160 psig as discussed in more detail hereafter.
- a condenser bypass conduit 27 which bridges between the refrigerant inlet and outlet ports 12a, 12b, respectively, of the condenser 12 includes a solonoid operated valve 28 therein which is actuated by a temperature sensor 30 positioned adjacent the water discharge port 12d of condenser 12.
- Valve 28 is a fail-safe valve which, in this embodiment, shuts off the heat exchanging condenser if water usage is so minimal that the water temperature reaches a severely high level.
- the pressure regulation valve 26 controls the flow of water through the condenser 12 to maintain a preset pressure, in this embodiment approximately 100-120 psig at the outlet port 12b of condenser 12. If the initial temperature of the water is about 155°C, water flow through the condenser will be minimized such that the water exit temperature therefrom approximates 38°C. The refrigerant temperature at outlet port 12b may then approximate 27°C.
- valve 26 gradually opens to allow greater water flow through the condenser 12 in order to maintain the pre-determined refrigerant pressure at. the condenser outlet 12b.
- the water flow through the condenser will be at its maximum when the inlet water temperature is approximately 39°C or above.
- the refrigerant may be maintained at approximately 49°C and 120 psig, and all of the heat rejected from the ice machine is absorbed into the water system.
- This heat includes the sensible heat from superheating the refrigerant vapor, the latent heat from condensing the refrigerant, and the sensible heat from subcooling the refrigerant liquid. Also since a water-cooled condenser has been utilized, the refrigerant discharge pressure-has been lower than the usual discharge pressure achieved when solely using an air-cooled condenser. With the high p res - sure refrigerant being an optimal value, which is lower than achievable with an air-cooled condenser, the machine has been operating more efficiently than heretofore-known ice machines of comparable size.
- the temperature or pressure of the refrigerant will be sufficiently high (approximating 49°C and 106 psig) to actuate the switch 18a and turn on the motor 18 of the air-cooled secondary condenser 17.
- the switch 18a cycles the fan on and off at approximately two-minute intervals.
- the additional condenser capacity in this embodiment acts to lower the refrigerant pressure to a satisfactory level approximating 120 psig, but nevertheless, to a level which is higher than the discharged pressure when the refrigerant-to-water condenser 12 was the sole heat rejection means in the system.
- the refrigerant-to-water condenser since the refrigerant-to-water condenser is still in the system, the refrigerant high side pressure is still lower and closer to optimum than if an air-cooled condenser alone were present in the system; thus, the system is still more efficient than a system solely using an air-cooled condenser.
- the dual condensers can no longer lower the refrigerant pressure to 120 psig and the air-cooled condenser motor 18 begins to run constantly rather than cyclicly. With the air-cooled condenser fan on constantly, the heat transferred to the water in the condenser 12 through desuper- heating will be added at a lower rate than previously described.
- the sensor 30 actuates the solenoid 28 to open the bypass line 27 allowing most of the hot refrigerant vapor to pass directly to the air-cooled condenser 17.
- An additional safety sensor 32 at the hot water storage tank 14 is capable of stopping the operation of the compressor 15 if the water temperature in the tank reaches an unsafe temperature, approximating 93°C. It should be noted that during normal operation both hot water usage and actual ice usage will, to some extent, determine the operation of the heat reclaiming device.
- the condenser 12 During normal operating hours, when both the ice machine and hot water system would be in use, the condenser 12 would be of sufficient size to handle all heat rejected by the ice machine. If the use of the external water supply should drop substantially or stop, in connection with an embodiment having a secondary air-cooled condenser, it may be expected that the secondary condenser would run in its cyclic phase during such extreme circumstances.
- the hot water storage tank 14 in accordance with another aspect of the invention, serves as a pre-heater which is positioned in the hot water system in parallel with a conventional hot water heater 44 such that the water supply inlet conduit 45 directs water into the storage tank where that water is mixed with heated water already in the tank.
- a modification of the system shown in connection with Figure 3 may include a second independent water-to-water condenser 40 or a second stage of condenser 12 may be positioned in the refrigeration unit to replace the air-cooled condenser 17.
- the water-cooled secondary condenser 40 would operate in a manner similar to air-cooled condenser 11 in that the pressure regulating valve 41 would not turn on a separate water cooling system, indicated by inlet conduit 42 and outlet conduit 43, until the primary refrigerant-to-water condenser 12 was operating at full heat reclaiming capacity.
- the commercial ice-maker and heat reclamation device combination of the present invention provides an efficient means of reclaiming the heat rejected from the refrigeration cycle of a commercial ice-making machine and transferring same to an external hot water supply.
- the system of the present invention provide an additional refrigeration device from which heat may be reclaimed, but the use of a refrigerant-to-water condenser in a commercial ice-maker coupled with a control system which is responsive to refrigerant condenser outlet pressure rather than temperature provides added efficiency to the commercial ice-making device while, at the same time, reclaiming the heat rejected from the refrigerant cycle.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Production, Working, Storing, Or Distribution Of Ice (AREA)
Abstract
Description
- The present invention relates generally to refrigerating machines, and more particularly to a commercial cube/ crushed ice-making machine.
- It has long been known that there is substantial heat rejection from a condenser in a conventional refrigeration unit consisting serially of a compressor, condenser, expansion valve and evaporator. Various devices and systems have been employed in attempts to utilise the rejected heat for purposes of heating fluids such as water and air. Embodiments of specific refrigeration systems and specific heat applications therefor are disclosed in the following United States Letters Patents; 3,926,008; 4,041,726; 3,922,876; 3,358,469; 3,513,663; and 2,739,452. Further, most heretofore known commercial ice-making machines with a capacity approximating 150 - 500 kgs. of ice per day have utilized air-cooled condensers, rather than more efficient water-cooled condensers, because an air-cooled condenser is cheaper and less bulky.
- Recent worldwide increases in fuel and energy costs have created a need for expanding the use of heat conservation and heat reclamation systems, with specialized refrigeration systems not heretofore considered for such use.
- Additionally, the prior known energy conservation systems which have been combined with refrigeration units have heretofore included controls which were responsive to changes in the temperatures of the refrigerant being cooled and the fluid being heated. While the temperature of the fluid being heated is an important parameter for control purposes, the temperature of the refrigerant in the condenser is important, but only secondarily to the efficiency of the refrigeration system. A prime factor in refrigeration efficiency is an optimum (not a maximum) pressure drop across the thermal expansion valve. None of the energy conservation systems heretofore known have disclosed a control system which optimizes the efficiency of the refrigeration unit while providing a controlled transfer of heat energy from the refrigeration condenser to an external air or water supply.
- We have noted that a substantial number of commercial ice-making machines are permanently installed for use in buildings such as motels, hotels, restaurants, etc. in close proximity to external water supplies in those buildinas, and have realized that in certain installations a refrigerant to water condensor may be used in a commercial ice-making machine and combined with or tapped into an adjacent external water supply to provide added efficiency to the ice-making machine and, at the same time, save energy by acting as a secondary heat source for the external water supply.
- It is one object of the present invention, generally stated, to provide for a refrigerating system having improved efficiency by including a heat reclaiming heat exchanger for heating an external water supply and an automated control for that heat exchanger.
- The control system is responsive to a refrigerant pressure in the condenser so as to maintain it at an optimum efficiency for the refrigeration system, as well as to the output water temperature from the condenser.
- More specifically, a refrigerator or ice-making machine has a closed loop refrigeration system including in series therein: a compressor, a refrigerant-to-water condenser whereby heat rejected from the closed loop system is transferred to the heat reclamation means through the condenser, an expansion valve, and an evaporator. The machine includes a control system having means responsive to both a refrigerant pressure in the condenser and a water temperature in the condenser for controlling heat exchanging water flow through the condenser while maintaining a pre-determined refrigerant pressure therein.
- This invention may best be understood by reference to the following description of presently preferred embodiments thereof taken in conjunction with the accompanying sheets of drawings, in which:-
- Figure 1 tis a perspective view of an ice-making machine including an embodiment of heat reclamation device operatively connected to an external water supply.
- Figure 2 is a perspective view of a modification of the heat reclamation device shown in Figure 1 including the addition of a hot water heater thereto.
- Figure 3 is a schematic diagram of the embodiment of refrigeration system, heat reclamation means, and a portion of an external water supply shown connected for operation, and
- Figure 4 is a fragmentary diagrammatic view of a water-cooled secondary condenser which may be substituted for the air-cooled secondary condenser shown in Figure 3.
- Referring to Figures 1 and 3, an ice-maker and heat reclamation system constructed in accordance with the present invention, and generally indicated at 10, includes a commercial ice-maker 11 such as sold under the trademark ROSS-TEMP, and an indirect heat reclamation device which is a refrigerant-to-
water condenser 12 which is conventional in itself and which, in this embodiment, is positioned externally of the ice-maker. Thecondenser 12 is preferably connected to a conventional external-water supply which, in this embodiment, is shown to include awater pump 13 and a hotwater storage tank 14 connected in series with the coolant side of thecondenser 12. - While any commercial ice-maker may be utilized in the system of the present invention, two commercial ice-making systems (neither shown) are ideally suited for use with the heat reclamation system of the present invention. In the first type, a layer of ice is formed on the bottom of a working sheet or plate. When the layer of ice has achieved a sufficient thickness, it is separated from the plate and dropped onto a heated grid or matrix. As the sheet of ice passes through the matrix, it is divided into ice cubes thereby. The second type of commercial ice-maker utilizes a hollow cylinder with ice being formed on an exterior surface thereof. An auger or the like is sleeved over the evaporator and includes a helical working edge which sweeps across the hollow cylindrical surface to shave ice therefrom in order to create "crushed" ice.
- As shown most clearly in Figure 3, the refrigeration system of the ice-maker 11 includes a
conventional refrigerant compressor 15 having a high pressure exhaust port 15a which is connected by conduit 16a to refrigerant inlet port 12a of theheat reclamation condenser 12. Therefrigerant cutlet port 12b is connected byconduit 16b to a secondary air-cooledcondenser 17 having acooling fan 18 and a fan control switch 18a associated therewith. A refrigerant receiver oraccumulator 19 is operatively positioned between the secondary condenser and athermal expansion valve 20 byconduits conventional evaporator 21 and conduit 16e are downstream of the valve and operatively connected via conduit 16f to a lowpressure inlet port 15b of the compressor. It can be appreciated that for ease of adaptability, the air-cooledsecondary condenser 17 may be the original equipment condenser for the separate ice-maker. If the refrigerant-to-water condenser 12 is mounted within the physical confines of the ice-maker 11, it is understood that it-could be sized to completely replace the secondary air-cooled condenser 11. The purpose of the secondary condenser will be discussed in connection with the operation of the system. In the embodiment shown in Figures 1 and 3, the water supply includes apump 13 which receives water from aninlet conduit 22 and pumps same throughoutlet conduit 23 to the water inlet port 12c of the refrigerant-to-water condenser 12 where the water is positioned in heat exchange relation with the high pressure refrigerant and passes out water outlet port 12d, through temperature actuatedsensor 30, andconduit 24 to the hotwater storage tank 14 where the water may be discharged throughconduit 25. - Depending upon the circumstances surrounding an individual installation, i.e., the size and amount of use of the ice-maker, and the size and use of the external water supply, the
condenser 12 may act as a primary or secondary heating source for the water supply. However, since the control system, to be discussed in detail below, does not provide for operation of the compressor if the ice machine is filled to capacity, it is assumed that in most installations thecondenser 12 will act as only a secondary heat source for the water supply. - In accordance with one aspect of the invention, the flow of water from
pump 13 into the refrigerant-to-water condenser 12 is regulated by avalve 26 which acts in response to the pressure of the refrigerant atoutlet 12b of the condenser. The operational pressure of the refrigerant proximately ranges from about 100 psig to about 160 psig as discussed in more detail hereafter. Additionally, a condenser bypass conduit 27 which bridges between the refrigerant inlet andoutlet ports 12a, 12b, respectively, of thecondenser 12 includes a solonoid operatedvalve 28 therein which is actuated by atemperature sensor 30 positioned adjacent the water discharge port 12d ofcondenser 12. Valve 28 is a fail-safe valve which, in this embodiment, shuts off the heat exchanging condenser if water usage is so minimal that the water temperature reaches a severely high level. - In operation, when the
ice machine compressor 15 is initially turned on, thepressure regulation valve 26 controls the flow of water through thecondenser 12 to maintain a preset pressure, in this embodiment approximately 100-120 psig at theoutlet port 12b ofcondenser 12. If the initial temperature of the water is about 155°C, water flow through the condenser will be minimized such that the water exit temperature therefrom approximates 38°C. The refrigerant temperature atoutlet port 12b may then approximate 27°C. - Depending upon the size of the external water system, as the inlet water temperature rises,
valve 26 gradually opens to allow greater water flow through thecondenser 12 in order to maintain the pre-determined refrigerant pressure at. thecondenser outlet 12b. In the embodiment shown, the water flow through the condenser will be at its maximum when the inlet water temperature is approximately 39°C or above. As long as the temperature in the water supply is approximately 39°C or less, the refrigerant may be maintained at approximately 49°C and 120 psig, and all of the heat rejected from the ice machine is absorbed into the water system. This heat includes the sensible heat from superheating the refrigerant vapor, the latent heat from condensing the refrigerant, and the sensible heat from subcooling the refrigerant liquid. Also since a water-cooled condenser has been utilized, the refrigerant discharge pressure-has been lower than the usual discharge pressure achieved when solely using an air-cooled condenser. With the high pres- sure refrigerant being an optimal value, which is lower than achievable with an air-cooled condenser, the machine has been operating more efficiently than heretofore-known ice machines of comparable size. - In the embodiment shown, as the water oin the external water supply rises in temperature above 38°C to approximately 43°C, the temperature or pressure of the refrigerant will be sufficiently high (approximating 49°C and 106 psig) to actuate the switch 18a and turn on the
motor 18 of the air-cooledsecondary condenser 17. Until such time as the inlet watdr temperature of water supply reaches approximately 52°C, the switch 18a cycles the fan on and off at approximately two-minute intervals.. The additional condenser capacity in this embodiment acts to lower the refrigerant pressure to a satisfactory level approximating 120 psig, but nevertheless, to a level which is higher than the discharged pressure when the refrigerant-to-water condenser 12 was the sole heat rejection means in the system. However, since the refrigerant-to-water condenser is still in the system, the refrigerant high side pressure is still lower and closer to optimum than if an air-cooled condenser alone were present in the system; thus, the system is still more efficient than a system solely using an air-cooled condenser. When the external water system temperature reaches approximately 59°C, the dual condensers can no longer lower the refrigerant pressure to 120 psig and the air-cooledcondenser motor 18 begins to run constantly rather than cyclicly. With the air-cooled condenser fan on constantly, the heat transferred to the water in thecondenser 12 through desuper- heating will be added at a lower rate than previously described. - When the condenser outlet water temperature in this embodiment reaches a preset maximum, approxi- mating 82°C, the
sensor 30 actuates thesolenoid 28 to open thebypass line 27 allowing most of the hot refrigerant vapor to pass directly to the air-cooledcondenser 17. Thus, heating in the external water system is stopped although the ice machine may continue to function. Anadditional safety sensor 32 at the hotwater storage tank 14 is capable of stopping the operation of thecompressor 15 if the water temperature in the tank reaches an unsafe temperature, approximating 93°C. It should be noted that during normal operation both hot water usage and actual ice usage will, to some extent, determine the operation of the heat reclaiming device. During normal operating hours, when both the ice machine and hot water system would be in use, thecondenser 12 would be of sufficient size to handle all heat rejected by the ice machine. If the use of the external water supply should drop substantially or stop, in connection with an embodiment having a secondary air-cooled condenser, it may be expected that the secondary condenser would run in its cyclic phase during such extreme circumstances. - Referring to Figure 2, in a second embodiment of the present invention, the hot
water storage tank 14, in accordance with another aspect of the invention, serves as a pre-heater which is positioned in the hot water system in parallel with a conventionalhot water heater 44 such that the water supply inlet conduit 45 directs water into the storage tank where that water is mixed with heated water already in the tank. There are two discharge conduits from the hot water storage tank 24a, afirst conduit 46 feeding thewater pump 13, and asecond conduit 47 feeding the water heater which has aconventional discharge conduit 48. Operation of this system is similar to the operation described above in connection with the first embodiment. - Referring to Figure 4, a modification of the system shown in connection with Figure 3 may include a second independent water-to-
water condenser 40 or a second stage ofcondenser 12 may be positioned in the refrigeration unit to replace the air-cooledcondenser 17. The water-cooledsecondary condenser 40 would operate in a manner similar to air-cooled condenser 11 in that the pressure regulating valve 41 would not turn on a separate water cooling system, indicated byinlet conduit 42 andoutlet conduit 43, until the primary refrigerant-to-water condenser 12 was operating at full heat reclaiming capacity. - Thus, the commercial ice-maker and heat reclamation device combination of the present invention provides an efficient means of reclaiming the heat rejected from the refrigeration cycle of a commercial ice-making machine and transferring same to an external hot water supply. Not only does the system of the present invention provide an additional refrigeration device from which heat may be reclaimed, but the use of a refrigerant-to-water condenser in a commercial ice-maker coupled with a control system which is responsive to refrigerant condenser outlet pressure rather than temperature provides added efficiency to the commercial ice-making device while, at the same time, reclaiming the heat rejected from the refrigerant cycle.
- While three particular variations of the invention have been shown and described, it will be obvious to those skilled in the art that changes and modifications may be made without departing from the invention in its broader aspects. .
Claims (10)
characterized in that the other side of the heat exchanger (12) is for inclusion in a hot water supply system (22, 23, 24, 14) and in that the control means includes both means (26) responsive to refrigerant pressure in the circuit between an outlet (12b) of the exchanger and the expansion means (20) and means (28, 30) responsive to the temperature of the water output from the exchanger (12
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
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DE8181300602T DE3171763D1 (en) | 1981-02-13 | 1981-02-13 | Energy conserving heat exchange apparatus for refrigerating machines, and refrigerating machine equipped therewith |
EP19810300602 EP0058259B1 (en) | 1981-02-13 | 1981-02-13 | Energy conserving heat exchange apparatus for refrigerating machines, and refrigerating machine equipped therewith |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP19810300602 EP0058259B1 (en) | 1981-02-13 | 1981-02-13 | Energy conserving heat exchange apparatus for refrigerating machines, and refrigerating machine equipped therewith |
Publications (2)
Publication Number | Publication Date |
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EP0058259A1 true EP0058259A1 (en) | 1982-08-25 |
EP0058259B1 EP0058259B1 (en) | 1985-08-14 |
Family
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19810300602 Expired EP0058259B1 (en) | 1981-02-13 | 1981-02-13 | Energy conserving heat exchange apparatus for refrigerating machines, and refrigerating machine equipped therewith |
Country Status (2)
Country | Link |
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EP (1) | EP0058259B1 (en) |
DE (1) | DE3171763D1 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
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EP1162419A1 (en) * | 2000-06-05 | 2001-12-12 | Denso Corporation | Hot-water supply system with heat pump cycle |
WO2011012153A1 (en) * | 2009-07-27 | 2011-02-03 | Ecolactis | Method and device for heat recovery on a vapour refrigeration system |
CN102353175A (en) * | 2011-08-12 | 2012-02-15 | 侯全舵 | Single pressing machine multifunctional heat pump device |
CN114294784A (en) * | 2021-12-28 | 2022-04-08 | 中山市爱美泰电器有限公司 | Defrosting control method for heat pump unit and heat pump unit |
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CA1048802A (en) * | 1976-12-06 | 1979-02-20 | Eds-Way Manufacturing Supply Limited | Heat reclaim unit |
DE2842841A1 (en) * | 1978-10-02 | 1980-04-17 | Eckerfeld Geb Maurer Erika | Combined hot water supply and refrigeration system - has heat exchanger double coil for refrigerant and for hot water supplied from separate tank |
US4226606A (en) * | 1978-10-06 | 1980-10-07 | Air & Refrigeration Corp. | Waste heat recovery system |
US4238931A (en) * | 1979-01-25 | 1980-12-16 | Energy Conservation Unlimited, Inc. | Waste heat recovery system controller |
-
1981
- 1981-02-13 EP EP19810300602 patent/EP0058259B1/en not_active Expired
- 1981-02-13 DE DE8181300602T patent/DE3171763D1/en not_active Expired
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DE2842841A1 (en) * | 1978-10-02 | 1980-04-17 | Eckerfeld Geb Maurer Erika | Combined hot water supply and refrigeration system - has heat exchanger double coil for refrigerant and for hot water supplied from separate tank |
US4226606A (en) * | 1978-10-06 | 1980-10-07 | Air & Refrigeration Corp. | Waste heat recovery system |
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Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1162419A1 (en) * | 2000-06-05 | 2001-12-12 | Denso Corporation | Hot-water supply system with heat pump cycle |
WO2011012153A1 (en) * | 2009-07-27 | 2011-02-03 | Ecolactis | Method and device for heat recovery on a vapour refrigeration system |
US20120151946A1 (en) * | 2009-07-27 | 2012-06-21 | Ecolactis | Method and device for heat recovery on a vapour refrigeration system |
US20170067677A1 (en) * | 2009-07-27 | 2017-03-09 | Ecolactis | Method and device for heat recovery on a vapour refrigeration system |
CN102353175A (en) * | 2011-08-12 | 2012-02-15 | 侯全舵 | Single pressing machine multifunctional heat pump device |
CN114294784A (en) * | 2021-12-28 | 2022-04-08 | 中山市爱美泰电器有限公司 | Defrosting control method for heat pump unit and heat pump unit |
Also Published As
Publication number | Publication date |
---|---|
EP0058259B1 (en) | 1985-08-14 |
DE3171763D1 (en) | 1985-09-19 |
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