EP0058259B1 - Echangeur de chaleur conservant de l'énergie pour des machines frigorifiques, et machine frigorifique pourvue d'un tel échangeur de chaleur - Google Patents

Echangeur de chaleur conservant de l'énergie pour des machines frigorifiques, et machine frigorifique pourvue d'un tel échangeur de chaleur Download PDF

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Publication number
EP0058259B1
EP0058259B1 EP19810300602 EP81300602A EP0058259B1 EP 0058259 B1 EP0058259 B1 EP 0058259B1 EP 19810300602 EP19810300602 EP 19810300602 EP 81300602 A EP81300602 A EP 81300602A EP 0058259 B1 EP0058259 B1 EP 0058259B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
water
heat
exchanger
refrigerating machine
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
Application number
EP19810300602
Other languages
German (de)
English (en)
Other versions
EP0058259A1 (fr
Inventor
Oscar M. Maring
Kenneth W. Schneider
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schneider Metal Manufacturing Co
Original Assignee
Schneider Metal Manufacturing Co
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Schneider Metal Manufacturing Co filed Critical Schneider Metal Manufacturing Co
Priority to EP19810300602 priority Critical patent/EP0058259B1/fr
Priority to DE8181300602T priority patent/DE3171763D1/de
Publication of EP0058259A1 publication Critical patent/EP0058259A1/fr
Application granted granted Critical
Publication of EP0058259B1 publication Critical patent/EP0058259B1/fr
Expired legal-status Critical Current

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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 heat exchangers for utilizing heat from the refrigerant of refrigerating machines, especially of a commercial cube/crushed ice-making machine, and to refrigerating machines equipped with such an exchanger.
  • CA ⁇ A ⁇ 1048802 shows a pressure sensitive valve system on the output side of a refrigerating machine, without combining it with a heat exchanger
  • US-A-4089667 shows a valved by-pass round a waterrefrigerant heat-exchanger
  • the control system is adapted to be responsive to refrigerant pressure at the outlet of the exchanger so as to maintain it at an optimum efficiency for the refrigeration system, as well as to the output water temperature from the condenser.
  • the heat exchanger may be combined with a refrigerating machine such as a refrigerator or ice-making machine having a closed loop refrigeration system of which the refrigerant side of the exchanger forms part; and the system may include 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.
  • a refrigerating machine such as a refrigerator or ice-making machine having a closed loop refrigeration system of which the refrigerant side of the exchanger forms part
  • the system may include 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.
  • 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 12 of the heat reclamation condenser 12.
  • the refrigerant outlet 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 17. 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 6,9 bar (100 psig) to about 11 bar (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 solenoid operated valve 28 therein which is actuated by temperature actuated 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 6,9-8,3 bar (100-120 psig) in the refrigerant at the outlet port 12b of condenser 12. If the initial temperature of the water is about 15.5°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 38°C or above.
  • the refrigerant may be maintained at approximately 49°C and 8,3 bar (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 pressure 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 7,3 bar (106 psig) to actuate the switch 18a and turn on the motor of the cooling fan 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 8,3 bar (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 8,3 bar (120 psig) and the fan motor the air-cooled condenser 17 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 desuperheating 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 17 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)

Claims (11)

1. Echangeur de chaleur conservant de l'énergie pour extraire la chaleur d'un fluide réfrigérant qui comprend un échangeur indirect de chaleur (12) eau/réfrigérant, dont une côté est pour le réfrigérant et l'autre côté est pour une inclusion dans un système d'alimentation en eau chaude (22, 23, 24, 14), et
un système de réglage réglant l'écoulement d'eau et du réfrigérant à travers ledit échangeur de chaleur eau/réfrigérant, caractérisé en ce que le système de réglage comprend un moyen (26) adapté à répondre à la pression du réfrigérant à une sortie du réfrigérant (12b) de l'échangeur (12) pour régler l'écoulement de l'eau à travers ledit échangeur de chaleur eau/réfrigérant et un moyen (30, 28) adapté à répondre à la température de l'eau à une sortie de l'eau (12b) de l'échangeur pour régler l'écoulement du réfrigérant à travers ledit échangeur de chaleur eau/ réfrigérant.
2. Machine frigorifique ayant un circuit de réfrigération en boucle fermée, ledit côté réfrigérant de l'échangeur de chaleur selon la revendication 1 étant dans ladite boucle fermée.
3. Machine frigorifique selon la revendication 2 caractérisée en ce que le circuit de réfrigération en boucle fermée (11) comprend en série un compresseur (15), ledit premier côté de l'échangeur indirect de chaleur eau/réfrigérant (12), un moyen détendeur (20) du réfrigérant et un évaporateur (12).
4. Echangeur de chaleur ou machine frigorifique selon la revendication 1, la revendication 2 ou la revendication 3 où le moyen sensible à la température (30, 28) du moyen de réglage sert à régler une gaine de bypass (27) du réfrigérant au-delà de l'échangeur (12).
5. Echangeur de chaleur ou machine frigorifique selon l'une quelconque des revendications précédentes où les moyens (26) répondant à la pression du moyen de réglage servent à régler le taux d'alimentation en eau vers une entrée d'eau (12c) de l'échangeur (12).
6. Echangeur de chaleur ou machine frigorifique selon l'une quelconque des revendications précédentes où il y a de plus au moins un échangeur de chaleur auxiliaire (17, 40) dans le circuit'en boucle fermée et où des moyens sensibles à la pression (18a, 41) de moyen de réglage servent à actionner l'échangeur de chaleur auxiliaire (17, 40).
7. Echangeur de chaleur ou machine frigorifique selon la revendication 5 où l'échangeur de chaleur auxiliaire est un condenseur (17) refroidi à l'air actionné par une opération par le moyen de réglage (18a) ou un ventilateur (18).
8. Echangeur de chaleur ou machine frigorifique selon la revendication 6 où l'échangeur de chaleur auxiliaire est un échangeur de chaleur (40) eau/réfrigérant actionné par une opération par le moyen de réglage (41) d'un système (42, 43) d'eau de refroidissement.
9. Echangeur de chaleur ou machine frigorifique selon l'une quelconque des revendications 6 à 8 où le moyen sensible à la pression (18a, 41) est adapté à une première gamme prédéterminée de pression à actionner l'échangeur de chaleur auxiliaire (17, 80) par intermittence.
10. Echangeur de chaleur ou machine frigorifique selon la revendication 9 où le moyen (18a, 41) est adapté à une seconde gamme prédéterminée de pressions supérieure à la première, à actionner continuellement l'échangeur auxiliaire de chaleur (17, 40).
11. Echangeur de chaleur ou machine frigorifique selon l'une quelconque des revendications précédentes où le moyen de réglage comprend un moyen sensible à la température (32) pour arrêter la machine frigorifique à une température prédéterminée de l'eau.
EP19810300602 1981-02-13 1981-02-13 Echangeur de chaleur conservant de l'énergie pour des machines frigorifiques, et machine frigorifique pourvue d'un tel échangeur de chaleur Expired EP0058259B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP19810300602 EP0058259B1 (fr) 1981-02-13 1981-02-13 Echangeur de chaleur conservant de l'énergie pour des machines frigorifiques, et machine frigorifique pourvue d'un tel échangeur de chaleur
DE8181300602T DE3171763D1 (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 (fr) 1981-02-13 1981-02-13 Echangeur de chaleur conservant de l'énergie pour des machines frigorifiques, et machine frigorifique pourvue d'un tel échangeur de chaleur

Publications (2)

Publication Number Publication Date
EP0058259A1 EP0058259A1 (fr) 1982-08-25
EP0058259B1 true EP0058259B1 (fr) 1985-08-14

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EP19810300602 Expired EP0058259B1 (fr) 1981-02-13 1981-02-13 Echangeur de chaleur conservant de l'énergie pour des machines frigorifiques, et machine frigorifique pourvue d'un tel échangeur de chaleur

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EP (1) EP0058259B1 (fr)
DE (1) DE3171763D1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3737381B2 (ja) * 2000-06-05 2006-01-18 株式会社デンソー 給湯装置
US20120151946A1 (en) * 2009-07-27 2012-06-21 Ecolactis Method and device for heat recovery on a vapour refrigeration system
CN102353175A (zh) * 2011-08-12 2012-02-15 侯全舵 单压机多功能热泵装置
CN114294784B (zh) * 2021-12-28 2023-08-01 中山市爱美泰电器有限公司 一种热泵机组除霜控制方法及热泵机组

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1854402A (en) * 1928-07-05 1932-04-19 Justus C Goosmann Refrigerating apparatus and control valve therefor
US1874803A (en) * 1931-01-12 1932-08-30 Reed Frank Maynard Heat exchange mechanism
US2356261A (en) * 1938-06-25 1944-08-22 Honeywell Regulator Co Refrigeration
US2181354A (en) * 1939-07-28 1939-11-28 Winters John Condenser for refrigerators
US2702671A (en) * 1951-03-13 1955-02-22 Detroit Controls Corp Differential temperature valve with pressure override
US2700279A (en) * 1952-06-12 1955-01-25 Gen Motors Corp Refrigerating apparatus and water heater
US2807145A (en) * 1953-12-10 1957-09-24 Ray M Henderson Apparatus for supplying heat for hot gas defrosting systems
US2952991A (en) * 1959-02-20 1960-09-20 Carrier Corp High side pressure control for refrigeration systems
DE1476954A1 (de) * 1965-03-18 1969-09-04 Walter Andreas Milchkuehlgeraet
US4089667A (en) * 1976-10-27 1978-05-16 Sun-Econ, Inc. Heat extraction or reclamation apparatus for refrigerating and air conditioning systems
FR2370424A1 (fr) * 1976-11-10 1978-06-09 Vironneau Pierre Procede et dispositif pour economiser l'energie dans les installations laitieres de traite
CA1048802A (fr) * 1976-12-06 1979-02-20 Eds-Way Manufacturing Supply Limited Recuperateur de chaleur
DE2712110C2 (de) * 1977-03-19 1985-02-07 Brown Boveri - York Kälte- und Klimatechnik GmbH, 6800 Mannheim Anlage zum Heizen und/oder Kühlen
US4134274A (en) * 1978-01-26 1979-01-16 The Trane Company System for producing refrigeration and a heated liquid and control therefor
DE2842841A1 (de) * 1978-10-02 1980-04-17 Eckerfeld Geb Maurer Erika Anordnung zur warmwasserbereitung
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

Also Published As

Publication number Publication date
DE3171763D1 (en) 1985-09-19
EP0058259A1 (fr) 1982-08-25

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