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US3851494A - Motor vehicle cooling system with bypass regulated heat exchanger - Google Patents

Motor vehicle cooling system with bypass regulated heat exchanger Download PDF

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Publication number
US3851494A
US3851494A US00377765A US37776573A US3851494A US 3851494 A US3851494 A US 3851494A US 00377765 A US00377765 A US 00377765A US 37776573 A US37776573 A US 37776573A US 3851494 A US3851494 A US 3851494A
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compressor
heat exchanger
refrigerant
cooling system
bypass
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US00377765A
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J Hess
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2507—Flow-diverting valves
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • 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

Definitions

  • This invention relates to a cooling system particularly suitable for use in a motor vehicle, of the type that uses a heat exchanger for further cooling of the liquified refrigerant passing from the condenser to the evaporator, which in so doing provides further warming of the cool vapor coming from the evaporator before it is supplied to the input of the compressor.
  • a cooling system of this type is described, for example, in the Handbuch der Kaltetechnik, by R. Plank (Vol. III, Heidelberg, 1959, Page 34 f.).
  • this cooling system the cool vapor is not sucked into the compressor in its original concentration, but only after it has been preheated in a heat exchanger which serves to provide supercooling of the liquid refrigerant.
  • This supercooling of the refrigerant before it reaches the expansion valve increases the cooling capability of the evaporator of the cooling system.
  • Increasing the preheating of the cooled vapor on its way to the compressor also raises the final temperature at the output of the compressor. The latter must not, however, exceed a certain value in the neighborhood of 150C.
  • the lubricating oil of the compressor partly dissolved in the refrigerant would .be charred.
  • the lubricant would lose its lubricating qualties and the compressor would soon fail in consequence.
  • the cooling system is installed in a motor vehicle, as shown, for example, in U.S. Pat. No. 2,893,700, the pipingfor the refrigerant must be provided in part by flexible hoses. If the compression temperature exceeds the above-mentioned limit, then, the flexible hoses are likely to be attacked to an extent that will eventually cause them to break.
  • a thermostatically controlled bypass is provided to reduce the temperature of the vapor input to the compressor.
  • a thermostatic control responds to the temperature of the compressor output and controls the bypass so as to prevent that temperature from rising to a value where it would be damaging to lubricant or hose materials.
  • the output of the condenser 2 is in turn coni I nected through an internal heat exchanger 3 and an expansion valve 4 to an evaporator 5.
  • a branching valve 6 At the output of the evaporator 5 is a branching valve 6 of three-sort twoposition type. The valve 6 in one position connects the output of the evaporator 5 with a pressure line 7 leading to the internal heat exchanger 3, while in the other position connects the output of the evaporator 5 with a bypass pressure line 8 that bypasses the internal heat exchanger 3. Both the bypass pressure line 8 and the pressure line passing through the internal heat exchanger 3 lead to the input suction line of the compressor l.
  • Temperature sensor 9 is provided in the refrigerant circulation path directly behind the compressor 1, i.e.
  • the sensor 9 controls thebranching valve 6.
  • the expansion valve 4 is connected with a temperature sensor 10, which is provided at the output of the evaporator 5.
  • Hoses of synthetic material appear, for example, at 20 and 21, forming part of the pressure lines in the refrigerant circulation system.
  • the cooling system of FIG. I operates as follows.
  • the compressor 1 is driven by a motor not shown in the drawing. In a motor vehicle the compressor could be driven by the crankshaft of the motor, by a belt drive for example.
  • the compressor 1 sucks in relatively cool vapor, compresses it and thereby warmsit.
  • the warm refrigerant is cooled in the condenser and thereby liquified.
  • the liquid refrigerant flows through the internal heat exchanger 3 and may be supercooled there, according to the position of the branching valve 6.
  • liquid refrigerant then flows to the expansion valve 4 where it is relieved of the condenser. pressure, down to the lower evaporator pressure. Under the lower pressure it enters the evaporator and there evaporates, while it absorbs heat from its surroundings. This heat absorption upon evaporation provides the cooling capacity of the cooling system.
  • the refrigerant is sucked out of the evaporator by the compressor 1, and according to the position of the branching valve 6 it is led through the internal heat exchanger 3 or through a bypass to be described presently.
  • the heat exchanger 3 a heat transfer occurs in the direction that causes the cool vapor drawn through by the compressor to be preheated.
  • the supercooling of the liquid refrigerant in the internal heat exchanger requires a considerable preheating of the refrigerant vapor applied to the input of the compressor 1, as the result of which the compression temperature naturally also rises.
  • the sensor 9 If it rises above the value for which the temperature sensor 9 is set, however, the sensor 9 then operates the branching valve 6 in the necessary direction to divert the cool vapor coming from the evaporator to the bypass pressure line 8 that bypasses the internal heat exchanger 3. Now that the cool vapor no longer value for which the temperature sensor 9 is set, so that the cool vapor coming from the evaporator can again be led through the internal heat exchanger 3, so that the coolingcapacity of the cooling system can again be raised.
  • the cooling system shown in H6. 2 likewise has a compressor 11, a condenser 12, a heat exchanger 13, an expansion valve 14 and an evaporator 15. Between the condenser 12 and the heat exchanger 13 there branches off a bypass 16 around the evaporator 15, and in this bypass 16 a second thermostatic expansion valve 17 is interposed. This expansionvalve 17 is connected with a temperature sensor 18, which again is situated in the refrigerant line directly behind the compressor 11 leading to the condenser 12.
  • this second embodiment of the invention in a cooling system corresponds substantially to the operation of the embodiment first described. If as a result of excessive preheating of the cool vapor drawn in by the compressor 11 the final compression temperature exceeds the value for which the temperature sensor 18 is set, the latter operates the second expansion valve 17 to spray additional refrigerant into the low pressure input line to the compressor, thereby reducing excessively high preheat temperatures at the compressor input. In consequence, the final compressor temperature will eventually fall back below the value for which the temperature sensor 18 is set.
  • a cooling system particularly suitable for a motor vehicle comprising a compressorfa condenser, a heat exchanger for further cooling of the liquidified refrigerant, an expansion valve and an evaporator arranged for continuously cycling the refrigerant, wherein:
  • said heat exchanger is arranged to cool said liquid refrigerant by warming cooled vapor from said evaporator before it is supplied to said compressor, and
  • automatically regulated bypass means are provided for reducing the temperature of the vapor provided to said compressor in response to thermostatic means responsive to the temperature of the refrigerant output of said compressor, and thereby to prevent the output of said compressor from reaching a temperature damaging to organic compounds exposed to the refrigerant of the system.
  • bypass means is a bypass around the vapor side (7) of said heat exchanger (3) controlled by a branching valve (6) for cutting said heat exchanger into and out of operation.
  • thermostatic means (9) is a temperature sensor in the refrigerant circulation path directly behind said compressor (1).
  • bypass means is a bypass around said evaporator (15) controlled by a second expansion valve (17) in response to thermostatic means (18) responsive to the temperature of the refrigerant output of said compressor (11).
  • thermostatic means (18) is a thermosensor in the refrigerant circulation path directly behind said compressor (ll

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

Excessive warming of the compressor input by the heat exchanger that supercools the condenser output is prevented by a bypass switched in and out by a thermostatic control at the output of the compressor to prevent the final compression temperature from rising to a value at which damage to lubricating materials and flexible hose materials would result. A branching valve or a second expansion valve may be used according to whether the bypass is just around the heat exchanger or around both the heat exchanger and the evaporator.

Description

ite tent [191 Hess tas
[ 1 MOTOR VEHICLE COOLING SYSTEM WITH BYPASS REGULATED HEAT EXCHANGER [75] Inventor: Jurgen Hess, Markgroningen,
Germany [73] Assignee: Robert Bosch GmbI-ll, Stuttgart,
Germany [22] Filed: July 9, 1973 [21] Appl. No.: 377,765
[30] I Foreign Application Priority Data Aug. 10, 1972 Germany 2239297 [52] US. Cl 62/196, 62/505, 62/513 [51] Int. Cl. F251) 41/00 [58] Field of Search 62/l96, 197, 198, 513,
[56] References Cited UNITED STATES PATENTS 2,402,802 6/1946 Carter 62/513 3,276,221 10/1966 Crumley 62/505 FOREIGN PATENTS OR APPLICATIONS 1,021,868 l/1958 Germany 62/513 Primary E.raminerMeyer Perlin Attorney, Agent, or Firm-William R. Woodward; Flynn & Frishauf 5 7 ABSTRACT Excessive warming of the compressor input by the heat exchanger that supercools the condenser output is prevented by a bypass switched in and out by a thermostatic control at the output of the compressor to prevent the final compression temperature from rising to a value at which damage to lubricating materials and flexible hose materials would result. A branching valve or a second expansion valve maybe used according to whether the bypass is just around the heat exchanger or around both the heat exchanger and the evaporator.
5 Claims, 2 Drawing Figures MOTOR VEHICLE COOLING SYSTEM WITH BYPASS REGULATED HEAT EXCHANGER This invention relates to a cooling system particularly suitable for use in a motor vehicle, of the type that uses a heat exchanger for further cooling of the liquified refrigerant passing from the condenser to the evaporator, which in so doing provides further warming of the cool vapor coming from the evaporator before it is supplied to the input of the compressor.
A cooling system of this type is described, for example, in the Handbuch der Kaltetechnik, by R. Plank (Vol. III, Heidelberg, 1959, Page 34 f.). In this cooling system the cool vapor is not sucked into the compressor in its original concentration, but only after it has been preheated in a heat exchanger which serves to provide supercooling of the liquid refrigerant. This supercooling of the refrigerant before it reaches the expansion valve increases the cooling capability of the evaporator of the cooling system. Increasing the preheating of the cooled vapor on its way to the compressor, however, also raises the final temperature at the output of the compressor. The latter must not, however, exceed a certain value in the neighborhood of 150C. If the final compression temperature should exceed that limit, the lubricating oil of the compressor partly dissolved in the refrigerant would .be charred. The lubricant would lose its lubricating qualties and the compressor would soon fail in consequence. Furthermore, if the cooling system is installed in a motor vehicle, as shown, for example, in U.S. Pat. No. 2,893,700, the pipingfor the refrigerant must be provided in part by flexible hoses. If the compression temperature exceeds the above-mentioned limit, then, the flexible hoses are likely to be attacked to an extent that will eventually cause them to break.
It is accordingly an object of the invention to provide a cooling system of the type described above, which permits the use of ordinary lubricants and also that of flexible hoses of rubber or synthetic materials as conduits for the refrigerant.
SUBJECT MATTER OF THE PRESENT INVENTION Briefly, a thermostatically controlled bypass is provided to reduce the temperature of the vapor input to the compressor. A thermostatic control responds to the temperature of the compressor output and controls the bypass so as to prevent that temperature from rising to a value where it would be damaging to lubricant or hose materials. It is particularly advantageous to provide the bypass around the vapor side of the heat exchanger and to have it controlled by a branching valve which can direct the vapor to the heat exchanger or to the bypass, according to the control provided by the thermosensor that provides the thermostatic action. On the other hand, it is also very advantageous to provide the bypass as a bypass around the evaporator, controlled by a second expansion valve that responds to the thermosensor providing the thermostatic action. In either case the best location for the thermosensor is in the refrigerant circulation path directly behind the compressor, that is, at or near its output connection.
Theinvention will be described by way of example with referenceto the accompanying drawing, wherein:
denser 2. The output of the condenser 2 is in turn coni I nected through an internal heat exchanger 3 and an expansion valve 4 to an evaporator 5. At the output of the evaporator 5 is a branching valve 6 of three-sort twoposition type. The valve 6 in one position connects the output of the evaporator 5 with a pressure line 7 leading to the internal heat exchanger 3, while in the other position connects the output of the evaporator 5 with a bypass pressure line 8 that bypasses the internal heat exchanger 3. Both the bypass pressure line 8 and the pressure line passing through the internal heat exchanger 3 lead to the input suction line of the compressor l.
Temperature sensor 9 is provided in the refrigerant circulation path directly behind the compressor 1, i.e.
in the pressure line leading from the compressor 1 to the condenser 2. The sensor 9 controls thebranching valve 6. The expansion valve 4 is connected with a temperature sensor 10, which is provided at the output of the evaporator 5. Hoses of synthetic material appear, for example, at 20 and 21, forming part of the pressure lines in the refrigerant circulation system.
The cooling system of FIG. I operates as follows. The compressor 1 is driven by a motor not shown in the drawing. In a motor vehicle the compressor could be driven by the crankshaft of the motor, by a belt drive for example. The compressor 1 sucks in relatively cool vapor, compresses it and thereby warmsit. The warm refrigerant is cooled in the condenser and thereby liquified. Now the liquid refrigerant flows through the internal heat exchanger 3 and may be supercooled there, according to the position of the branching valve 6. The
liquid refrigerant then flows to the expansion valve 4 where it is relieved of the condenser. pressure, down to the lower evaporator pressure. Under the lower pressure it enters the evaporator and there evaporates, while it absorbs heat from its surroundings. This heat absorption upon evaporation provides the cooling capacity of the cooling system.
The refrigerant is sucked out of the evaporator by the compressor 1, and according to the position of the branching valve 6 it is led through the internal heat exchanger 3 or through a bypass to be described presently. In the heat exchanger 3 a heat transfer occurs in the direction that causes the cool vapor drawn through by the compressor to be preheated. The supercooling of the liquid refrigerant in the internal heat exchanger requires a considerable preheating of the refrigerant vapor applied to the input of the compressor 1, as the result of which the compression temperature naturally also rises. If it rises above the value for which the temperature sensor 9 is set, however, the sensor 9 then operates the branching valve 6 in the necessary direction to divert the cool vapor coming from the evaporator to the bypass pressure line 8 that bypasses the internal heat exchanger 3. Now that the cool vapor no longer value for which the temperature sensor 9 is set, so that the cool vapor coming from the evaporator can again be led through the internal heat exchanger 3, so that the coolingcapacity of the cooling system can again be raised.
The cooling system shown in H6. 2 likewise has a compressor 11, a condenser 12, a heat exchanger 13, an expansion valve 14 and an evaporator 15. Between the condenser 12 and the heat exchanger 13 there branches off a bypass 16 around the evaporator 15, and in this bypass 16 a second thermostatic expansion valve 17 is interposed. This expansionvalve 17 is connected with a temperature sensor 18, which again is situated in the refrigerant line directly behind the compressor 11 leading to the condenser 12.
The operation of this second embodiment of the invention in a cooling system corresponds substantially to the operation of the embodiment first described. If as a result of excessive preheating of the cool vapor drawn in by the compressor 11 the final compression temperature exceeds the value for which the temperature sensor 18 is set, the latter operates the second expansion valve 17 to spray additional refrigerant into the low pressure input line to the compressor, thereby reducing excessively high preheat temperatures at the compressor input. In consequence, the final compressor temperature will eventually fall back below the value for which the temperature sensor 18 is set.
I claim:
1. A cooling system particularly suitable for a motor vehicle, comprising a compressorfa condenser, a heat exchanger for further cooling of the liquidified refrigerant, an expansion valve and an evaporator arranged for continuously cycling the refrigerant, wherein:
said heat exchanger is arranged to cool said liquid refrigerant by warming cooled vapor from said evaporator before it is supplied to said compressor, and
automatically regulated bypass means are provided for reducing the temperature of the vapor provided to said compressor in response to thermostatic means responsive to the temperature of the refrigerant output of said compressor, and thereby to prevent the output of said compressor from reaching a temperature damaging to organic compounds exposed to the refrigerant of the system.
2. A cooling system as defined in claim 1, in which said bypass means is a bypass around the vapor side (7) of said heat exchanger (3) controlled by a branching valve (6) for cutting said heat exchanger into and out of operation.
3. A cooling system as defined in claim 2, in which said thermostatic means (9) is a temperature sensor in the refrigerant circulation path directly behind said compressor (1).
4. A cooling system as defined in claim 1, in which said bypass means is a bypass around said evaporator (15) controlled by a second expansion valve (17) in response to thermostatic means (18) responsive to the temperature of the refrigerant output of said compressor (11).
5. A cooling system as defined in claim 4, in which said thermostatic means (18) is a thermosensor in the refrigerant circulation path directly behind said compressor (ll

Claims (5)

1. A cooling system particularly suitable for a motor vehicle, comprising a compressor, a condenser, a heat exchanger for further cooling of the liquidified refrigerant, an expansion valve and an evaporator arranged for continuously cycling the refrigerant, wherein: said heat exchanger is arranged to cool said liquid refrigerant by warming cooled vapor from said evaporator before it is supplied to said compressor, and automatically regulated bypass means are provided for reducing the temperature of the vapor provided to said compressor in response to thermostatic means responsive to the temperature of the refrigerant output of said compressor, and thereby to prevent the output of said compressor from reaching a temperature damaging to organic compounds exposed to the refrigerant of the system.
2. A cooling system as defined in claim 1, in which said bypass means is a bypass around the vapor side (7) of said heat exchanger (3) controlled by a branching valve (6) for cutting said heat exchanger into and out of operation.
3. A cooling system as defined in claim 2, in which said thermostatic means (9) is a temperature sensor in the refrigerant circulation path directly behind said compressor (1).
4. A cooling system as defined in claim 1, in which said bypass means is a bypass around said evaporator (15) controlled by a second expansion valve (17) in response to thermostatic means (18) responsive to the temperature of the refrigerant output of said compressor (11).
5. A cooling system as defined in claim 4, in which said thermostatic means (18) is a thermosensor in the refrigerant circulation path directly behind said compressor (11).
US00377765A 1972-08-10 1973-07-09 Motor vehicle cooling system with bypass regulated heat exchanger Expired - Lifetime US3851494A (en)

Applications Claiming Priority (1)

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DE2239297A DE2239297A1 (en) 1972-08-10 1972-08-10 REFRIGERATION SYSTEM, IN PARTICULAR FOR USE IN A MOTOR VEHICLE

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BR (1) BR7306105D0 (en)
DE (1) DE2239297A1 (en)
ES (1) ES417708A1 (en)
FR (1) FR2195779B1 (en)
IT (1) IT993704B (en)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4259848A (en) * 1979-06-15 1981-04-07 Voigt Carl A Refrigeration system
US4270359A (en) * 1978-12-07 1981-06-02 Hummel Steven L Solar heating system
WO1981002923A1 (en) * 1980-04-07 1981-10-15 S Samek Refrigeration method and apparatus using heat
US4359879A (en) * 1980-12-31 1982-11-23 Diversified Air Products, Inc. Refrigeration system and novel heat exchanger therefor
US4428853A (en) 1981-10-19 1984-01-31 Institut Francais Du Petrole Process for the heating and/or thermal conditioning of a building by means of a heat pump operated with a specific mixture of working fluids
US4577468A (en) * 1985-01-04 1986-03-25 Nunn Jr John O Refrigeration system with refrigerant pre-cooler
US4899555A (en) * 1989-05-19 1990-02-13 Carrier Corporation Evaporator feed system with flash cooled motor
US4918942A (en) * 1989-10-11 1990-04-24 General Electric Company Refrigeration system with dual evaporators and suction line heating
DE3911270A1 (en) * 1989-04-07 1990-10-11 Licentia Gmbh Domestic refrigerating appliance
US4974427A (en) * 1989-10-17 1990-12-04 Copeland Corporation Compressor system with demand cooling
US5289699A (en) * 1991-09-19 1994-03-01 Mayer Holdings S.A. Thermal inter-cooler
US5809791A (en) * 1996-01-22 1998-09-22 Stewart, Iii; Thomas Ray Remora II refrigeration process
WO2001063187A1 (en) * 2000-02-22 2001-08-30 E-Pak Technology, Inc. Refrigeration system and method of operation therefor
US6330805B1 (en) 1997-09-16 2001-12-18 Francois Galian Method of operating a refrigerating unit with a refrigerant fluid circuit
US20090120114A1 (en) * 2007-11-12 2009-05-14 Ingersoll-Rand Company Compressor with flow control sensor
WO2017207526A1 (en) * 2016-05-31 2017-12-07 Eaton Industrial IP GmbH & Co. KG Cooling system
US20180195806A1 (en) * 2017-01-11 2018-07-12 Hanon Systems Plastic material internal heat exchanger
CN113945025A (en) * 2020-07-15 2022-01-18 比泽尔制冷设备有限公司 Refrigerant compressor

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2402802A (en) * 1944-02-17 1946-06-25 Detroit Lubricator Co Refrigerating apparatus
DE1021868B (en) * 1955-03-31 1958-01-02 Waggon U Maschinenfabriken G M Device for the operation of refrigeration systems
US3276221A (en) * 1965-02-05 1966-10-04 Ernest W Crumley Refrigeration system

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2402802A (en) * 1944-02-17 1946-06-25 Detroit Lubricator Co Refrigerating apparatus
DE1021868B (en) * 1955-03-31 1958-01-02 Waggon U Maschinenfabriken G M Device for the operation of refrigeration systems
US3276221A (en) * 1965-02-05 1966-10-04 Ernest W Crumley Refrigeration system

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4270359A (en) * 1978-12-07 1981-06-02 Hummel Steven L Solar heating system
US4259848A (en) * 1979-06-15 1981-04-07 Voigt Carl A Refrigeration system
WO1981002923A1 (en) * 1980-04-07 1981-10-15 S Samek Refrigeration method and apparatus using heat
US4359879A (en) * 1980-12-31 1982-11-23 Diversified Air Products, Inc. Refrigeration system and novel heat exchanger therefor
US4428853A (en) 1981-10-19 1984-01-31 Institut Francais Du Petrole Process for the heating and/or thermal conditioning of a building by means of a heat pump operated with a specific mixture of working fluids
US4468337A (en) * 1981-10-19 1984-08-28 Institut Francais Du Petrole Process for the heating and/or thermal conditioning of a building by means of a heat pump operated with a specific mixture of working fluids
US4577468A (en) * 1985-01-04 1986-03-25 Nunn Jr John O Refrigeration system with refrigerant pre-cooler
DE3911270A1 (en) * 1989-04-07 1990-10-11 Licentia Gmbh Domestic refrigerating appliance
US4899555A (en) * 1989-05-19 1990-02-13 Carrier Corporation Evaporator feed system with flash cooled motor
US4918942A (en) * 1989-10-11 1990-04-24 General Electric Company Refrigeration system with dual evaporators and suction line heating
US4974427A (en) * 1989-10-17 1990-12-04 Copeland Corporation Compressor system with demand cooling
US5289699A (en) * 1991-09-19 1994-03-01 Mayer Holdings S.A. Thermal inter-cooler
US5809791A (en) * 1996-01-22 1998-09-22 Stewart, Iii; Thomas Ray Remora II refrigeration process
US6330805B1 (en) 1997-09-16 2001-12-18 Francois Galian Method of operating a refrigerating unit with a refrigerant fluid circuit
WO2001063187A1 (en) * 2000-02-22 2001-08-30 E-Pak Technology, Inc. Refrigeration system and method of operation therefor
US6539732B2 (en) 2000-02-22 2003-04-01 E-Pak Technology, Inc. Refrigeration system and method of operation therefor
US6644068B2 (en) 2000-02-22 2003-11-11 E-Pak Technology, Inc. Refrigeration system and method of operation therefor
US20090120114A1 (en) * 2007-11-12 2009-05-14 Ingersoll-Rand Company Compressor with flow control sensor
US7762789B2 (en) 2007-11-12 2010-07-27 Ingersoll-Rand Company Compressor with flow control sensor
WO2017207526A1 (en) * 2016-05-31 2017-12-07 Eaton Industrial IP GmbH & Co. KG Cooling system
CN109477674A (en) * 2016-05-31 2019-03-15 伊顿智能动力有限公司 cooling system
US20180195806A1 (en) * 2017-01-11 2018-07-12 Hanon Systems Plastic material internal heat exchanger
US10775106B2 (en) * 2017-01-11 2020-09-15 Hanon Systems Plastic material internal heat exchanger
CN113945025A (en) * 2020-07-15 2022-01-18 比泽尔制冷设备有限公司 Refrigerant compressor
CN113945025B (en) * 2020-07-15 2023-08-04 比泽尔制冷设备有限公司 Refrigerating medium compressor

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Publication number Publication date
FR2195779B1 (en) 1976-09-17
IT993704B (en) 1975-09-30
BR7306105D0 (en) 1974-08-29
FR2195779A1 (en) 1974-03-08
DE2239297A1 (en) 1974-02-21
ES417708A1 (en) 1976-02-16

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