EP0180904A2 - Dispositif de refroidissement - Google Patents

Dispositif de refroidissement Download PDF

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Publication number
EP0180904A2
EP0180904A2 EP85113773A EP85113773A EP0180904A2 EP 0180904 A2 EP0180904 A2 EP 0180904A2 EP 85113773 A EP85113773 A EP 85113773A EP 85113773 A EP85113773 A EP 85113773A EP 0180904 A2 EP0180904 A2 EP 0180904A2
Authority
EP
European Patent Office
Prior art keywords
cooling device
suction
subcooler
line
refrigerant
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
EP85113773A
Other languages
German (de)
English (en)
Other versions
EP0180904B1 (fr
EP0180904A3 (en
Inventor
Hermann Renz
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.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
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 Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Priority to AT85113773T priority Critical patent/ATE46026T1/de
Publication of EP0180904A2 publication Critical patent/EP0180904A2/fr
Publication of EP0180904A3 publication Critical patent/EP0180904A3/de
Application granted granted Critical
Publication of EP0180904B1 publication Critical patent/EP0180904B1/fr
Expired 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/074—Details of compressors or related parts with multiple cylinders
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • 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
    • F25B2600/2509—Economiser valves

Definitions

  • the invention relates to a cooling device with a piston compressor having a plurality of cylinders, a condenser, an expansion element and an evaporator, with a line connecting the piston compressor, the condenser, the expansion element and the evaporator to one another for an evaporable refrigerant liquid, and with an in the line between the condenser and expansion element, provided with a vaporizable coolant subcooler for the refrigerant.
  • the object is achieved in that part of the refrigerant is used as the coolant for the subcooler, and an outlet opening of the subcooler for evaporated coolant is connected via an additional suction line to the suction side of part of the cylinders of the piston compressor.
  • a multi-cylinder, motor-driven compressor 1 sucks vapor Refrigerant via a so-called suction line 2 from an evaporator 3 at a relatively low pressure and compresses the steam to a relatively high pressure in order to convey it via a so-called compressed gas line 4 into a condenser 5.
  • a heat transfer medium for example air, water or the like
  • the liquefied (and slightly subcooled) refrigerant is passed via a liquid line 6 to an expansion device 7, the function of which is to feed an amount of refrigerant liquid adapted to the respective operating conditions into the evaporator 3.
  • the expansion element 7 is also a throttling point between high and low pressure.
  • the liquid refrigerant fed into the evaporator 3 and kept at low pressure evaporates by supplying heat and is then sucked off again by the compressor 1 via the suction line 2, either dry saturated or slightly overheated.
  • cooling capacity the amount of heat absorbed in the evaporator 3
  • the subcooler 8 has its own coolant circuit with compressor 11, suction line 12, pressure line 14,
  • the circuit of the subcooler 8 also contains a solenoid valve 19.
  • the refrigerant circuit connected to the compressor 1 is also referred to as the main circuit, the coolant circuit connected to the compressor 11 as a secondary circuit. Both circuits work physically in the same way.
  • the delivery volume of the compressor 11 required for the secondary or subcooling circuit need only be approximately 10 to 25% of the delivery volume of the compressor 1 in order to achieve the desired liquid subcooling.
  • the core of which is a compressor which combines the functions of the compressors 1 and 11.
  • the common piston compressor 21 has six cylinders. Of these six cylinders, only a few (e.g. five cylinders) draw vaporous refrigerant via the suction line 22 from the evaporator 23 and, in the same way as previously described with reference to the main circuit of FIG. 1, convey via the compressed gas line 24 into the common condenser 25. After leaving the condenser 25, the liquefied refrigerant is passed directly through the subcooler 28 to the expansion element 27 via a first line A of the liquid line 26 and is fed by the latter into the evaporator 23 in a controlled manner and, after evaporation, is sucked off again by the piston compressor 21.
  • a few e.g. five cylinders
  • a partial flow of the liquefied refrigerant is fed into the subcooler 28 in a controlled manner via a further line B of the liquid line 26 via a remotely controlled solenoid valve 29 and through a further expansion element 30.
  • the refrigerant evaporates due to this partial stream of the heat supply by the relatively warmer K älteschierikeit of the strand A and is then used as an additional suction vapor, with an outlet opening 31 of the subcooler 28 pumped connected suction line 32.
  • This pumping takes place according to the invention via the cylinder or cylinders of the piston compressor 21-, the suction chambers of which are not connected to the line 22 but to the line 32. From the suction side of this or these cylinders, the suction steam is then conveyed to a common pressure chamber of the piston compressor 21 and mixed there with the steam of the main compressor part (originating from the suction line 22). This process causes the refrigerant liquid to be subcooled in the subcooler 8 with the aforementioned increase in performance resulting therefrom.
  • FIG. 3 shows a modified arrangement in which the subcooler 38 is designed as an "open liquid collector", ie does not act as a heat exchanger like the subcooler 28 in the case of FIG. 2. Corresponding parts are provided with the same reference numerals in FIGS. 2 and 3.
  • the principle of operation of the "open" subcooler 38 is based on the fact that part of the liquid refrigerant contained therein is sucked off in vapor form by the relevant part of the compressor 21 via the additional suction line 32.
  • the K included in the sub-cooler 38 älteffentechnik is subcooled thereby.
  • the solenoid valve 29 has the task of interrupting the refrigerant flow during the standstill periods and is opened with a certain delay after the start.
  • a regulator 39 in the additional suction line 32 controls the pressure and the flowing amount of refrigerant.
  • a pressure regulator 4o is provided in the system according to FIG. 3, which is required to maintain a certain condensing pressure.
  • FIG. 4 shows one of the twin cylinder heads.
  • the other cylinder heads of the compressor are designed in the usual way.
  • the suction chamber of the cylinder head shown in FIG. 4 is divided into two suction chambers 42 and 43 by a partition 41.
  • the chamber 42 is connected to the subcooler via the additional suction line 32 in the manner described.
  • the suction chamber 43 like the suction chambers of the other cylinders, is connected to the evaporator 23 via the suction line 22.
  • One of the pistons 44 of the compressor is visible in FIG. 3. All cylinders of the arrangement are connected to a common pressure chamber (not shown) in the usual way.
  • a valve device 45 is arranged in the partition 41, which is designed either (as shown) as a check valve 46 or as a solenoid valve can be.
  • the compressor compressor 21
  • the subcooler is first pumped down to a suction pressure that corresponds to that of the other cylinders.
  • the check valve opens automatically, the cylinder in question then works in parallel with the other compressor part.
  • valve device 41 as a solenoid valve, this must already be opened when the solenoid valve 29 closes.
  • the cooling device described offers the following advantages: at the start, the system can initially stabilize by delayed opening of the solenoid valve 29. The risk of refrigerant transfer from the subcooler to the compressor during the Start-up phase is avoided by the aforementioned empty pumping. By switching the supercooling circuit on and off, power control is possible without affecting the application limits. By combining the main circuit with its secondary circuit, there is no need for second compressors and condensers with accessories. This also results in a simplified line assembly. A subsequent retrofitting of the compressor to the embodiment according to FIG. 4 is possible.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Surgical Instruments (AREA)
  • Encapsulation Of And Coatings For Semiconductor Or Solid State Devices (AREA)
  • Sampling And Sample Adjustment (AREA)
EP85113773A 1984-11-03 1985-10-29 Dispositif de refroidissement Expired EP0180904B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85113773T ATE46026T1 (de) 1984-11-03 1985-10-29 Kuehlvorrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843440253 DE3440253A1 (de) 1984-11-03 1984-11-03 Kuehlvorrichtung
DE3440253 1984-11-03

Publications (3)

Publication Number Publication Date
EP0180904A2 true EP0180904A2 (fr) 1986-05-14
EP0180904A3 EP0180904A3 (en) 1986-10-08
EP0180904B1 EP0180904B1 (fr) 1989-08-30

Family

ID=6249455

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85113773A Expired EP0180904B1 (fr) 1984-11-03 1985-10-29 Dispositif de refroidissement

Country Status (3)

Country Link
EP (1) EP0180904B1 (fr)
AT (1) ATE46026T1 (fr)
DE (2) DE3440253A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2092424A1 (es) * 1992-09-16 1996-11-16 Ornaque Carlos Gutierrez Sistema frigorico de seguridad por bloque mixto.
EP0898128A2 (fr) * 1997-08-22 1999-02-24 Carrier Corporation Pompe à chaleur à compression internement étagée et à fluide frigorigène variable
EP0837291A3 (fr) * 1996-08-22 2000-10-04 Denso Corporation Système frigorifique du type à compression de vapeur
EP1139039A1 (fr) * 2000-03-27 2001-10-04 Carrier Corporation Amélioration d'un circuit d'économiseur
EP1498667A2 (fr) * 2003-07-18 2005-01-19 Star Refrigeration Ltd. Système de réfrigération améliore a cycle transcritique
WO2005008148A1 (fr) * 2003-07-14 2005-01-27 Carrier Corporation Systeme de compression de fluide frigorigene a sous-refroidissement selectif
WO2006015741A1 (fr) * 2004-08-09 2006-02-16 Linde Kältetechnik Gmbh Circuit frigorifique et procede de fonctionnement d'un circuit frigorifique
DE102005009173A1 (de) * 2005-02-17 2006-08-24 Bitzer Kühlmaschinenbau Gmbh Kälteanlage
US8113008B2 (en) 2004-08-09 2012-02-14 Carrier Corporation Refrigeration circuit and method for operating a refrigeration circuit

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4702086A (en) * 1986-06-11 1987-10-27 Turbo Coils Inc. Refrigeration system with hot gas pre-cooler
US5095712A (en) * 1991-05-03 1992-03-17 Carrier Corporation Economizer control with variable capacity
DE19826291A1 (de) * 1998-06-12 1999-12-16 Linde Ag Verfahren zum Betreiben einer Pumpe zur Förderung siedender Kältemittel oder Kälteträger
DK3295029T3 (da) 2015-05-13 2019-09-23 Carrier Corp Frem- og tilbagegående economiserkompressor

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH101888A (de) * 1922-06-26 1923-10-16 Sulzer Ag Verbund-Kompressions-Kältemaschine.
US2320097A (en) * 1941-08-20 1943-05-25 Servel Inc Refrigeration
FR2287666A1 (fr) * 1974-10-11 1976-05-07 Primore Sales Inc Soupape automatique munie d'un compresseur de refrigerant
FR2304041A1 (fr) * 1975-03-11 1976-10-08 Kvaerner Brug Kjoleavdelning Dispositif pour une installation de compression et de condensation de gaz
US4197719A (en) * 1976-01-29 1980-04-15 Dunham-Bush, Inc. Tri-level multi-cylinder reciprocating compressor heat pump system
US4230470A (en) * 1977-01-21 1980-10-28 Hitachi, Ltd. Air conditioning system
FR2503841A1 (fr) * 1981-04-09 1982-10-15 Guillemin Georges Pompe a chaleur pour le chauffage de batiments
DE3301304A1 (de) * 1982-02-26 1983-09-15 Hitachi, Ltd., Tokyo Kuehlanlage mit einem kompressor in spiralbauweise

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH101888A (de) * 1922-06-26 1923-10-16 Sulzer Ag Verbund-Kompressions-Kältemaschine.
US2320097A (en) * 1941-08-20 1943-05-25 Servel Inc Refrigeration
FR2287666A1 (fr) * 1974-10-11 1976-05-07 Primore Sales Inc Soupape automatique munie d'un compresseur de refrigerant
FR2304041A1 (fr) * 1975-03-11 1976-10-08 Kvaerner Brug Kjoleavdelning Dispositif pour une installation de compression et de condensation de gaz
US4197719A (en) * 1976-01-29 1980-04-15 Dunham-Bush, Inc. Tri-level multi-cylinder reciprocating compressor heat pump system
US4230470A (en) * 1977-01-21 1980-10-28 Hitachi, Ltd. Air conditioning system
FR2503841A1 (fr) * 1981-04-09 1982-10-15 Guillemin Georges Pompe a chaleur pour le chauffage de batiments
DE3301304A1 (de) * 1982-02-26 1983-09-15 Hitachi, Ltd., Tokyo Kuehlanlage mit einem kompressor in spiralbauweise

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2092424A1 (es) * 1992-09-16 1996-11-16 Ornaque Carlos Gutierrez Sistema frigorico de seguridad por bloque mixto.
EP0837291A3 (fr) * 1996-08-22 2000-10-04 Denso Corporation Système frigorifique du type à compression de vapeur
EP0898128A2 (fr) * 1997-08-22 1999-02-24 Carrier Corporation Pompe à chaleur à compression internement étagée et à fluide frigorigène variable
EP0898128A3 (fr) * 1997-08-22 2001-09-05 Carrier Corporation Pompe à chaleur à compression internement étagée et à fluide frigorigène variable
EP1139039A1 (fr) * 2000-03-27 2001-10-04 Carrier Corporation Amélioration d'un circuit d'économiseur
WO2005008148A1 (fr) * 2003-07-14 2005-01-27 Carrier Corporation Systeme de compression de fluide frigorigene a sous-refroidissement selectif
EP1498667A3 (fr) * 2003-07-18 2006-05-17 Star Refrigeration Ltd. Système de réfrigération améliore a cycle transcritique
EP1498667A2 (fr) * 2003-07-18 2005-01-19 Star Refrigeration Ltd. Système de réfrigération améliore a cycle transcritique
US7845190B2 (en) 2003-07-18 2010-12-07 Star Refrigeration Limited Transcritical refrigeration cycle
WO2006015741A1 (fr) * 2004-08-09 2006-02-16 Linde Kältetechnik Gmbh Circuit frigorifique et procede de fonctionnement d'un circuit frigorifique
US8113008B2 (en) 2004-08-09 2012-02-14 Carrier Corporation Refrigeration circuit and method for operating a refrigeration circuit
US8844303B2 (en) 2004-08-09 2014-09-30 Carrier Corporation Refrigeration circuit and method for operating a refrigeration circuit
US9476614B2 (en) 2004-08-09 2016-10-25 Carrier Corporation Refrigeration circuit and method for operating a refrigeration circuit
US9494345B2 (en) 2004-08-09 2016-11-15 Carrier Corporation Refrigeration circuit and method for operating a refrigeration circuit
DE102005009173A1 (de) * 2005-02-17 2006-08-24 Bitzer Kühlmaschinenbau Gmbh Kälteanlage
WO2006087075A1 (fr) * 2005-02-17 2006-08-24 Bitzer Kühlmaschinenbau Gmbh Appareil frigorifique
US7451617B2 (en) 2005-02-17 2008-11-18 Bitzer Kuhlmaschinenbau Gmbh Refrigeration system

Also Published As

Publication number Publication date
DE3572721D1 (en) 1989-10-05
EP0180904B1 (fr) 1989-08-30
ATE46026T1 (de) 1989-09-15
DE3440253A1 (de) 1986-05-15
EP0180904A3 (en) 1986-10-08

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