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EP0180904B1 - Dispositif de refroidissement - Google Patents

Dispositif de refroidissement Download PDF

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Publication number
EP0180904B1
EP0180904B1 EP85113773A EP85113773A EP0180904B1 EP 0180904 B1 EP0180904 B1 EP 0180904B1 EP 85113773 A EP85113773 A EP 85113773A EP 85113773 A EP85113773 A EP 85113773A EP 0180904 B1 EP0180904 B1 EP 0180904B1
Authority
EP
European Patent Office
Prior art keywords
supercooler
cooling
liquefier
suction pipe
liquid
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
EP85113773A
Other languages
German (de)
English (en)
Other versions
EP0180904A3 (en
EP0180904A2 (fr
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 according to the preamble of patent claim 1.
  • a cooling device of this type is known from US-A-4197 719.
  • the structure of the known device is complicated, it requires complex external control and requires special compressors to which existing cooling devices cannot normally be easily converted.
  • the invention has for its object to improve a generic device so that with a simple design of the device, the switch from one to two-stage mode of operation takes place automatically and a subsequent installation of the automatic reversing device is possible with existing cooling devices.
  • FR-A-2 503 841 is a heat pump. known for heating buildings, but there is a two-stage expansion with only one-stage compressor. Thermodynamically, there is no gain whatsoever in the case of two-stage expansion versus single-stage expansion, since in this known heat pump a regulator relaxes the intermediate pressure back to suction pressure.
  • a multi-cylinder, motor-driven compressor 1 sucks vaporous refrigerant out of an evaporator 3 at a relatively low pressure via a so-called suction line 2 and compresses the steam to a relatively high pressure in order to draw it over a so-called compressed gas line 4 in a condenser 5 to promote.
  • 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.
  • the subcooler 8 is assigned its own coolant circuit with compressor 11, suction line 12, pressure line 14, condenser 15, liquid line 16 and expansion element 17, the subcooler 8 acting as an evaporator and cooling the refrigerant in line 6.
  • 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 and the coolant circuit connected to the compressor 11 as a secondary circuit. Both circuits function 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 from the evaporator 23 via the suction line 22 and deliver them via the compressed gas line in the same way as previously described with reference to the main circuit of FIG. 1 24 into the common condenser 25.
  • the liquefied refrigerant, after exiting the condenser 25, is led via a first line A of the liquid line 26 directly through the subcooler 28 to the expansion element 27 and is fed by this regulated into the evaporator 23 and after evaporation from the piston compressor 21 vacuumed again.
  • 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 of this partial flow evaporates due to the supply of heat by the relatively warmer refrigerant liquid of the strand A and is then pumped out as suction steam via an additional suction line 32 connected to an outlet opening 31 of the subcooler 28.
  • 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 in the subcooler 8 to be subcooled with the resultant product already mentioned. Performance increase.
  • 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 from. relevant part of the compressor 21 is sucked off in vapor form via the additional suction line 32. The refrigerant liquid contained in the subcooler 38 is thereby subcooled.
  • 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 40 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 of a four, six or eight cylinder compressor in V, W or WW design.
  • 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 can either be designed (as shown) as a check valve 46 or as a solenoid valve.
  • 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: when starting, the system can initially stabilize by delaying the opening of the solenoid valve 29. The risk of refrigerant shifting 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.

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  • 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)
  • Encapsulation Of And Coatings For Semiconductor Or Solid State Devices (AREA)
  • Sampling And Sample Adjustment (AREA)
  • Surgical Instruments (AREA)

Claims (6)

1. Dispositif de refroidissement comprenant un compresseur à piston (21) à plusieurs cylindres, un condenseur (25), un organe d'expansion (27) et un évaporateur (23), avec une canalisation (22, 24, 26) de fluide frigorifique évaporable reliant entre eux le compresseur à piston, le condenseur, l'organe d'expansion et l'évaporateur, et avec un surrefroidisseur (28, 38) du fluide frigorifique prévu sur la conduite (26) entre le condenseur et l'organe d'expansion et fonctionnant avec un fluide réfrigérant évaporable, dans lequel une partie du fluide frigorifique est utilisée comme fluide réfrigérant du surrefroidisseur, l'ouverture de sortie (31) du surrefroidisseur étant reliée par une conduite d'aspiration (32) supplémentaire au côté aspiration d'une partie des cylindres du compresseur à piston, et dans lequel en outre, soit une partie du liquide frigorifique est prélevée et déviée après le condenseur pour passer à travers un organe d'expansion (30) supplémentaire, puis par le surrefroidisseur analogue à un échangeur de chaleur (28) et de là elle est conduite à la conduite d'aspiration supplémentaire, soit le surrefroidisseur est analogue à un récipient séparateur gaz-liquide (38) raccordé à la conduite d'aspiration supplémentaire, dans lequel par suite de l'abaissement de la pression une partie du liquide frigorifique dévié se vaporise et refroidit la fraction restante du fluide, caractérisé en ce qu'une chambre d'aspiration (42) de l'un au moins des cylindres du compresseur à piston (21), reliée à la conduite d'aspiration (32) supplémentaire, est séparée par une cloison de séparation (41) des chambres d'aspiration (43) des autres cylindres, et un dispositif à clapet (45) est disposé dans la cloison de séparation et en ce que ce dispositif à clapet se ferme quand la pression dans la chambre d'aspiration (42) reliée à la conduite d'aspiration supplémentaire est supérieure à celle des autres chambres d'aspiration (43).
2. Dispositif de refroidissement selon la revendication 1, caractérisé en ce que le dispositif à clapet (45) est un clapet anti-retour.
3. Dispositif de refroidissement selon la revendication 1, caractérisé en ce que le dispositif à clapet (45) est une électrovanne.
4. Dispositif de refroidissement selon une quelconque des revendications 1 à 3, caractérisé en ce qu'une électrovanne (29) est montée en amont de l'organe d'expansion (30) supplémentaire.
5. Dispositif de refroidissement selon une quelconque des revendications 1 à 3, caractérisé en ce qu'une électrovanne (20) est disposée sur la conduite d'aspiration (32) supplémentaire.
6. Dispositif de refroidissement selon une quelconque des revendications 1 à 3, caractérisé en ce qu'un régulateur de pression (40) est prévu entre le condenseur (25) et le surrefroidisseur (38).
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 EP0180904A2 (fr) 1986-05-14
EP0180904A3 EP0180904A3 (en) 1986-10-08
EP0180904B1 true 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 (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3295029B1 (fr) 2015-05-13 2019-07-03 Carrier Corporation Compresseur à va-et-vient économisé

Families Citing this family (12)

* 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
ES2092424B1 (es) * 1992-09-16 1997-07-01 Ornaque Carlos Gutierrez Sistema frigorifico de seguridad por bloque mixto.
EP0837291B1 (fr) * 1996-08-22 2005-01-12 Denso Corporation Système frigorifique du type à compression de vapeur
US5848537A (en) * 1997-08-22 1998-12-15 Carrier Corporation Variable refrigerant, intrastage compression heat pump
DE19826291A1 (de) * 1998-06-12 1999-12-16 Linde Ag Verfahren zum Betreiben einer Pumpe zur Förderung siedender Kältemittel oder Kälteträger
US6374631B1 (en) * 2000-03-27 2002-04-23 Carrier Corporation Economizer circuit enhancement
US6820434B1 (en) * 2003-07-14 2004-11-23 Carrier Corporation Refrigerant compression system with selective subcooling
ATE464516T1 (de) * 2003-07-18 2010-04-15 Star Refrigeration Verbesserte überkritische kältekreislaufanlage
DK1794510T3 (da) 2004-08-09 2012-05-21 Carrier Corp CO2 kølekredsløb med underkøling af det flydende kølemiddel med receiver-flashgassen samt fremgangsmåde til drift af dette
DE102004038640A1 (de) * 2004-08-09 2006-02-23 Linde Kältetechnik GmbH & Co. KG Kältekreislauf und Verfahen zum Betreiben eines Kältekreislaufes
DE102005009173A1 (de) * 2005-02-17 2006-08-24 Bitzer Kühlmaschinenbau Gmbh Kälteanlage

Family Cites Families (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
US4026122A (en) * 1974-10-11 1977-05-31 Primore Sales, Inc. Refrigeration system
NO136427C (no) * 1975-03-11 1977-08-31 Kvaerner Brug Kjoleavdelning Anordning ved anlegg til komprimering og kondensering av gasser.
US4197719A (en) * 1976-01-29 1980-04-15 Dunham-Bush, Inc. Tri-level multi-cylinder reciprocating compressor heat pump system
GB1595616A (en) * 1977-01-21 1981-08-12 Hitachi Ltd Air conditioning system
FR2503841A1 (fr) * 1981-04-09 1982-10-15 Guillemin Georges Pompe a chaleur pour le chauffage de batiments
JPS58148290A (ja) * 1982-02-26 1983-09-03 Hitachi Ltd スクロ−ル圧縮機を用いた冷凍装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3295029B1 (fr) 2015-05-13 2019-07-03 Carrier Corporation Compresseur à va-et-vient économisé

Also Published As

Publication number Publication date
EP0180904A3 (en) 1986-10-08
DE3440253A1 (de) 1986-05-15
ATE46026T1 (de) 1989-09-15
EP0180904A2 (fr) 1986-05-14
DE3572721D1 (en) 1989-10-05

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