EP0255035A2 - Circuit frigorifique - Google Patents

Circuit frigorifique Download PDF

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Publication number
EP0255035A2
EP0255035A2 EP87110619A EP87110619A EP0255035A2 EP 0255035 A2 EP0255035 A2 EP 0255035A2 EP 87110619 A EP87110619 A EP 87110619A EP 87110619 A EP87110619 A EP 87110619A EP 0255035 A2 EP0255035 A2 EP 0255035A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
refrigeration circuit
condenser
evaporator
compressor
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
Application number
EP87110619A
Other languages
German (de)
English (en)
Other versions
EP0255035A3 (en
EP0255035B1 (fr
Inventor
Sato Motoharu
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.)
Sanden Corp
Original Assignee
Sanden Corp
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 Sanden Corp filed Critical Sanden Corp
Publication of EP0255035A2 publication Critical patent/EP0255035A2/fr
Publication of EP0255035A3 publication Critical patent/EP0255035A3/en
Application granted granted Critical
Publication of EP0255035B1 publication Critical patent/EP0255035B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion 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
    • F25B2500/00—Problems to be solved
    • F25B2500/15—Hunting, i.e. oscillation of controlled refrigeration variables reaching undesirable values
    • 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
    • F25B2600/19—Refrigerant outlet condenser temperature

Definitions

  • This invention relates to a refrigeration circuit for use in an automotive air conditioning system, and more particularly, to a refrigeration circuit which includes a control device for controlling the flow amount of refrigerant.
  • the refrigeration circuit generally comprises a compressor 1, condenser 2, receiver drier 3, decompression device 4 and evaporator 5.
  • a thermostatic expansion valve is utilized in the circuit as decompression device to control the flow amount and expansion of the refrigerant.
  • the operation of expansion valve 4 is dependent on the degree of superheat at the outlet side of evaporator 5.
  • the refrigeration circuit is usually operated within the range of superheat five through eight degrees at the outlet side of evaporator 5 to prevent reduction of efficiency of compressor 1, damage of valves of compressor 1 and the like due to liquid compression.
  • FIG. 2 Another conventional refrigeration circuit is disclosed in Fig. 2 and the conventional refrigeration circuit includes compressor 1, condenser 2, decompression device 6, for example a capillary, an orifice or the like, evaporator 5 and accumulator 7.
  • Each component of the refrigeration circuit is connected with each other in series and the order as mentioned above. Since accumulator 7 is connected to the outlet side of evaporator 5, the degree of superheat at the outlet side of evaporator 5 is always near zero. Therefore, the heat exchange efficiency of evaporator 5 is improved.
  • the refrigeration circuit includes a compressor, a condenser, an evaporator and an accumulator so that discharging refrigerant from a compressor passes through the condenser, the evaporator and the accumulator, respectively, and returns to a suction port of the compressor.
  • a subcooling control valve is connected to the condenser and coupled to the evaporator through a fixed throttle valve so as to control a flow amount of refrigerant due to detecting a subcooling value of refrigerant at an outlet side of the condenser.
  • the fixed throttle valve is directly conneted to the subcooling control valve so as to control changes of the flow amount of refrigerant flowing into the evaporator.
  • the refrigeration circuit of the present invention comprises compressor 10, condenser 11, subcooling control valve 12, decompression device, for example a capillary or an orifice 13, evaporator 14 and accumulator 15.
  • the condenser 11 is connected to the outlet port of compressor 10 and also coupled to the capillary 13 through subcooling control valve 12.
  • the evaporator 14 is connected to the capillary 13 and also coupled to the inlet port of compressor 10 through the accumulator 15.
  • Control device 21 which has the function of the subcooling control valve 12 and capillary 13 is shown.
  • Control device 21 comprises a tubular casing 211 which includes inlet tube 212 and outlet tube 213, an operating valve 214 which is disposed in the connecting portion between inlet tube 212 and outlet tube 213, the diaphragm 215, and sensing cylinder 216.
  • An opening 217 is formed through the inlet tube 212, and the operating valve 214 is urged so as to close the opening 217 by adjusting a spring 218.
  • An orifice 223 is formed on the outlet tube 213.
  • a valve seat 219 which is disposed on an upper space 221 of casing 211 and attached on one end surface of diaphragm 215, is coupled to the base of the operating valve 214 through a connecting rod 220.
  • the diaphragm 215 divides the upper space 221 into two chambers 221a, 221b, and and one chamber 221a, in which the valve seat 219 is disposed, is in communication with the interior of inlet tube 212 through communication channel 222.
  • the other chamber 221b communicates with the interior of the sensing cylinder 216. Refrigerant is enclosed in the sensing cylinder 216 so as to detect the temperature and to operate the diaphragm 215.
  • the control device 21 detects the temperature of the refrigerant at the outlet side of condenser 11 by the sensing cylinder 216, i.e., the conduit between condenser 11 and control device 21 is in contact with the sensing cylinder 216.
  • the refrigerant in the sensing cylinder 216 is changing its aspect from fluid into gas or from gas into fluid in accordance with the temperature of refrigerant at the outlet side of the condenser 11. In accordance with the change of temperature of the refrigerant, the saturation pressure of the refrigerant in the sensing cylinder 216 is thus changed.
  • the control device 21 is operated in accordance with the counterbalance among the satura­tion pressure of refrigerant in the sensing cylinder 216, the pressure of the refrigerant at the outlet side of the condenser 11 and the recoil strength of the adjusting spring 218.
  • control device 21 detects the subcooling value, i.e., the difference between the actual temperature of refrigerant and the saturation temperature at the same pressure of refrigerant at the outlet side of the condenser 11 is less than the predetermined subcooling value, which is determined by adjusting spring 218, i.e., the amount of the saturation pressure in the sensing cylinder 216 and the recoil strength of the adjusting spring 218 is less than the pressure of refrigerant at the outlet side of condenser 11, the operating valve 214 is urged upwardly, and the opening 217 of inlet tube 212 is opened. Thereafter, since the amount of refrigerant at the outlet side of the condenser 11 is increased, the temperature of refrigerant is thus gradually increased.
  • the predetermined subcooling value which is determined by adjusting spring 218, i.e., the amount of the saturation pressure in the sensing cylinder 216 and the recoil strength of the adjusting spring 218 is less than the pressure of refrigerant at the outlet side of con
  • the saturation pressure of refrigerant in the sensing cylinder 126 is gradually raised together with the increase of the temperature of refrigerant at the outlet side of condenser 11, and the diaphragm 215 operates so as to close the opening 217 of inlet tube 212 against the recoil strength of adjusting spring 218.
  • the operating valve 214 adjusts the area of opening 217 up to a position where the amount of the saturation pressure in sensing cylinder 216 and the recoil strength of adjusting spring 218 is equal to the pressure of refrigerant at the outlet side of condenser 11.
  • the orifice 213 controls changes of the flow amount of refrigerant which flows into the evaporator 14.
  • FIG. 5 the relationship between the refrigerating capacity of an evaporator and the rotational speed of a compressor is shown.
  • a dotted curve shows the refrigerating capacity with respect to the refrigeration circuit which includes an expansion valve as shown in Fig. 1.
  • a lined and dotted curve shows the refrigerating capacity with respect to the refrigeration circuit which includes a capillary as shown in Fig. 2.
  • a solid curve shows the refrigerating capacity with respect to the refrigeration circuit in accordance with one embodiment of this invention as shown in Fig. 3.
  • the refrigeration circuit according to one embodiment of this invention has higher refrigerating capacity than the conventional refrigeration circuit including a capillary and almost equal refrigerating capacity to the refrigeration circuit including an expansion valve.
  • the refrigeration circuit according to one embodiment of this invention has the suitable refrigerating capacity which is positioned between the refrigerating capacities in accordance with the conventional refrigeration circuit including an expansion valve or a capillary.
  • control device 21 As a modification of control device 21 as shown in Fig. 4, another control device may be used which operates in accordance with detecting signals sent from sensors sensing the pressure and temperature of refrigerant at the outlet side of condenser 11 in the refrigeration circuit.
  • the diaphragm 215 may be replaced by a bellows, and also orifice 223 may be replaced by a capillary as a fixed throttle valve mechanism having the same function.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP87110619A 1986-07-23 1987-07-22 Circuit frigorifique Expired - Lifetime EP0255035B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP171714/86 1986-07-23
JP61171714A JPS6329165A (ja) 1986-07-23 1986-07-23 冷凍サイクルの冷媒制御装置

Publications (3)

Publication Number Publication Date
EP0255035A2 true EP0255035A2 (fr) 1988-02-03
EP0255035A3 EP0255035A3 (en) 1989-11-15
EP0255035B1 EP0255035B1 (fr) 1991-09-11

Family

ID=15928314

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87110619A Expired - Lifetime EP0255035B1 (fr) 1986-07-23 1987-07-22 Circuit frigorifique

Country Status (5)

Country Link
EP (1) EP0255035B1 (fr)
JP (1) JPS6329165A (fr)
KR (1) KR960002567B1 (fr)
AU (1) AU599120B2 (fr)
DE (1) DE3772894D1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5205131A (en) * 1991-03-19 1993-04-27 White Consoldiated Industries, Inc. Refrigerator system with subcooling flow control
WO1999013277A1 (fr) * 1997-09-05 1999-03-18 Fisher & Paykel Limited Systeme de refrigeration a sous refroidissement variable
FR2774461A1 (fr) * 1998-01-30 1999-08-06 Valeo Climatisation Dispositif de climatisation, notamment de l'habitacle d'un vehicule automobile, comportant une boucle de fluide refrigerant
FR2780143A1 (fr) * 1998-06-23 1999-12-24 Valeo Climatisation Boucle de fluide refrigerant amelioree pour installation de climatisation de vehicule
EP0987505A3 (fr) * 1998-09-18 2001-12-05 TGK Co., Ltd. Vanne d'expansion du type à commande du degré de surrefroidissement

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2603682B2 (de) * 1976-01-31 1977-11-24 Danfoss A/S, Nordborg (Dänemark) Ventilanordnung fuer kaelteanlagen
US4136528A (en) * 1977-01-13 1979-01-30 Mcquay-Perfex Inc. Refrigeration system subcooling control
US4193781A (en) * 1978-04-28 1980-03-18 Mcquay-Perfex Inc. Head pressure control for heat reclaim refrigeration systems
DE3229779A1 (de) * 1981-08-12 1983-04-28 Mitsubishi Denki K.K., Tokyo Kuehlsystem mit nebenkuehlung zum steuern des kaeltemittelstromes
EP0147855A2 (fr) * 1983-12-28 1985-07-10 Kabushiki Kaisha Saginomiya Seisakusho Système frigorifique

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5577677A (en) * 1978-12-08 1980-06-11 Nippon Denso Co Refrigerating plant
JPS58205060A (ja) * 1982-05-26 1983-11-29 株式会社東芝 冷凍サイクル
JPS60178768U (ja) * 1984-05-07 1985-11-27 サンデン株式会社 冷凍回路

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2603682B2 (de) * 1976-01-31 1977-11-24 Danfoss A/S, Nordborg (Dänemark) Ventilanordnung fuer kaelteanlagen
US4136528A (en) * 1977-01-13 1979-01-30 Mcquay-Perfex Inc. Refrigeration system subcooling control
US4193781A (en) * 1978-04-28 1980-03-18 Mcquay-Perfex Inc. Head pressure control for heat reclaim refrigeration systems
DE3229779A1 (de) * 1981-08-12 1983-04-28 Mitsubishi Denki K.K., Tokyo Kuehlsystem mit nebenkuehlung zum steuern des kaeltemittelstromes
EP0147855A2 (fr) * 1983-12-28 1985-07-10 Kabushiki Kaisha Saginomiya Seisakusho Système frigorifique

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5205131A (en) * 1991-03-19 1993-04-27 White Consoldiated Industries, Inc. Refrigerator system with subcooling flow control
WO1999013277A1 (fr) * 1997-09-05 1999-03-18 Fisher & Paykel Limited Systeme de refrigeration a sous refroidissement variable
US6351950B1 (en) 1997-09-05 2002-03-05 Fisher & Paykel Limited Refrigeration system with variable sub-cooling
FR2774461A1 (fr) * 1998-01-30 1999-08-06 Valeo Climatisation Dispositif de climatisation, notamment de l'habitacle d'un vehicule automobile, comportant une boucle de fluide refrigerant
FR2780143A1 (fr) * 1998-06-23 1999-12-24 Valeo Climatisation Boucle de fluide refrigerant amelioree pour installation de climatisation de vehicule
EP0987505A3 (fr) * 1998-09-18 2001-12-05 TGK Co., Ltd. Vanne d'expansion du type à commande du degré de surrefroidissement
US6532764B1 (en) 1998-09-18 2003-03-18 Tgk Co., Ltd. Degree of supercooling control type expansion valve

Also Published As

Publication number Publication date
JPS6329165A (ja) 1988-02-06
AU7602487A (en) 1988-01-28
EP0255035A3 (en) 1989-11-15
EP0255035B1 (fr) 1991-09-11
DE3772894D1 (de) 1991-10-17
AU599120B2 (en) 1990-07-12
KR960002567B1 (ko) 1996-02-22
KR880001990A (ko) 1988-04-28

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