EP0077414B1 - Luftklimatisierungssystem - Google Patents

Luftklimatisierungssystem Download PDF

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Publication number
EP0077414B1
EP0077414B1 EP81108580A EP81108580A EP0077414B1 EP 0077414 B1 EP0077414 B1 EP 0077414B1 EP 81108580 A EP81108580 A EP 81108580A EP 81108580 A EP81108580 A EP 81108580A EP 0077414 B1 EP0077414 B1 EP 0077414B1
Authority
EP
European Patent Office
Prior art keywords
compressor
solenoid valve
heat exchanger
refrigerant
valve
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
EP81108580A
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English (en)
French (fr)
Other versions
EP0077414A1 (de
Inventor
Fumio C/O Mitsubischi Denki K. K. Matsuoka
Hitoshi C/O Mitsubischi Denki K. K. Iijima
Original Assignee
Mitsubishi Electric Corp
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Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to DE8585100213T priority Critical patent/DE3177054D1/de
Priority to EP81108580A priority patent/EP0077414B1/de
Priority to DE8181108580T priority patent/DE3175833D1/de
Publication of EP0077414A1 publication Critical patent/EP0077414A1/de
Application granted granted Critical
Publication of EP0077414B1 publication Critical patent/EP0077414B1/de
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
    • F25B13/00—Compression machines, plants or systems, with 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting

Definitions

  • the present invention relates to an air temperature conditioning system, comprising a compressor, a first heat exchanger, expansion means, and a second heat exchanger connected in series with each other; and means for repeatedly starting and stopping said compressor in response to room temperature sensing means.
  • the conventional refrigeration cycle apparatus includes a compressor, a condenser, an expansion device such as a capillary tube or an expansion valve, and an evaporator with these components sequentially coupled in series with each other.
  • the compressor When the compressor is stopped, the pressure of the refrigerant on a high pressure side is balanced with the pressure of the refrigerant on the low pressure side.
  • the compressor As the compressor is started, the difference between the pressures of the high pressure side and the low pressure side is gradually increased until the apparatus is brought to an ordinary operating state.
  • the compressor is accordingly repeatedly started and stopped, the high pressure side refrigerant is balanced in presence with the low pressure side refrigerant each time the apparatus is stopped. During these times, refrigerant liquid stored on the low pressure side in an evaporator is drawn into the compressor.
  • the presence of the liquid refrigerant in the condenser increases the load on the compressor at the time of restarting the compressor. This lowers the coefficient of performance (hereinafter abbreviated as "COP") of the apparatus as
  • the apparatus should retain refrigerant separately distributed on the high pressure side and low pressure side without mixture thereof when the compressor is stopped thus to eliminate a loss of energy produced at the time of restarting the compressor in the conventional apparatus and to thereby improve the efficiency thereof and to make it possible to attain an ordinary operating state in a short time after the compressor is restarted.
  • a solution to this problem is suggested by CH-A-188 957.
  • a valve is provided for isolating the high pressure side of the compressor from the low pressure side when the compressor is stopped.
  • An object of the invention is to provide an air temperature conditioning system which incorporates a series connection of a compressor, first and second heat exchangers, and an expansion device in which heating operation may be continued with one heat exchanger whilst performing the operation of defrosting the other heat exchanger.
  • an air temperature conditioning system comprising a compressor, a first heat exchanger, expansion means, and a second heat exchanger connected in series with each other; and means for repeatedly starting and stopping said compressor in response to room temperature sensing means; characterised by: means for isolating refrigerant on a high pressure side of said compressor from refrigerant on a lower pressure side of said compressor when said compressor is stopped; and diverting means for passing refrigerant from the compressor to the second heat exchanger for defrosting said second heat exchanger while continuing a heating operation with said first heat exchanger.
  • Reference numeral 1 designates generally a compressor.
  • a refrigerant gas compressed at high temperature and high pressure by the compressor 1 is fed through a check valve 2 and a four-way valve 3 into a condenser 7.
  • the refrigerant dissipates heat in the condenser 7 and is condensed to a high temperature and high pressure liquid.
  • the refrigerant liquid is then passed through an expansion valve 6 where the refrigerant becomes a low temperature, low pressure liquid and a solenoid valve 5, which acts as a switching valve, and from there is introduced into an evaporator 4.
  • the low temperature and low pressure refrigerant liquid in the evaporator 4 absorbs heat and thus evaporates to a gas.
  • This refrigerant gas is again fed through the four-way valve 3 into an accumulator 8 which isolates the refrigerant liquid which cannot be evaporated in the evaporator 4 and is retained in the liquid state and which returns only the refrigerant gas again to the compressor 1. While the compressor 1 is operating, the apparatus continuously performs the refrigeration cycle.
  • Reference numeral 10 illustrates a fan for the condenser 7 and 9 a fan for the evaporator 4.
  • the four-way valve 3 is a change-over or switching valve which operates so that the condenser 7 can be used as an evaporator and the evaporator 4 used as a condenser.
  • the evaporator 4 is used as an outdoor side heat exchanger, and the condenser 7 is used as an indoor side heat exchanger.
  • the apparatus is operated in a refrigeration cycle in which the four-way valve 3 is switched so that the outdoor side heat exchanger is used as a condenser and the indoor side heat exchanger is used as an evaporator.
  • the air temperature conditioning system operates to detect the temperature in the room by a temperature detector or thermostat (not shown) and to start or stop the compressor 1 so as to maintain the room temperature at a set temperature by operating or stopping the refrigeration cycle apparatus.
  • the solenoid valve 5, which isolates the compressor 1, is constructed so as to open when the compressor 1 is started and to close when the compressor 1 is stopped.
  • the solenoid valve 5 and the check valve 2 function to isolate high pressure side refrigerant and low pressure side refrigerant when the compressor 1 is stopped.
  • the high pressure side refrigerant in the refrigeration cycle is isolated from the low pressure side refrigerant. Since the solenoid valve 5 is only then opened, a desired pressure difference between the high and low pressure side refrigerant can be attained in short time and the apparatus can reach the ordinary operating state in short time.
  • a conventional refrigerant cycle not incorporating such an isolating device requires about five minutes to reach the ordinary operation state after restarting.
  • the refrigeration cycle apparatus of the invention requires only about one minute and twenty seconds to make the transition.
  • the aforesaid switching element is not limited to the solenoid valve 5 but may also be another type of switching valve and may be any type which closes when the compressor 1 is stopped and opens when the compressor 1 is started.
  • the four-way valve 3 is, as illustrated, positioned to connect the indoor heat exchanger 7 as a condenser and the outdoor heat exchanger 4 as an evaporator. Further, there is provided a refrigerant bypass tube 21 extending between the outlet of the compressor 1 and the inlet of the outdoor side heat exchanger 4. A second solenoid valve 22 is disposed in the bypass tube 21 for opening or closing the bypass tube 21. The second solenoid valve 22 is operated to be open during the starting of the defrosting operation of the outdoor side heat exchanger and to close at the end of the defrosting operation of the outdoor side heat exchanger in the heating mode.
  • the second solenoid valve 22 provided in the bypass passage 21 is normally closed in the heating mode, and the high temperature and high pressure refrigerant gas compressed by the compressor 1 passes through the check valve 2 and is introduced from the four-way valve 3 into the indoor side heat exchanger 7 which dissipates heat to the atmosphere to condense the refrigerant gas and to a high pressure and high temperature refrigerant liquid.
  • the refrigerant liquid becomes low pressure and lowtemperature refrigerant at the expansion valve 6 and is introduced through the solenoid valve 5 into the outdoor side heat exchanger 4 which absorbs heat from the atmosphere to evaporate the refrigerant liquid.
  • the refrigerant gas thus evaporated is again introduced through the four-way valve 3 and the accumulator 8 into the compressor 1 to complete one cycle. The same cycle is continuously repeated.
  • the solenoid valve 5 opens when the compressor 1 is started and closes when the compressor 1 is stopped, as mentioned above, to thus isolate the high pressure side refrigerant and the lower pressure side refrigerant. Accordingly, the COP of the compressor 1 is improved.
  • the solenoid valve 5 may be closed by a defrost operation command signal while simultaneously the second solenoid valve 22 in the bypass passage 21 is opened.
  • the high temperature and high pressure refrigerant gas in the indoor side heat exchanger 7 continues to condense to become high temperature and high pressure refrigerant liquid while dissipating heat.
  • the high temperature and high pressure refrigerant gas compressed by the compressor 1 is introduced into the outdoor side heat exchanger 4through the bypass tube 21 to thereby defrost the outdoor side heat exchanger by applying heat thereto to melt the frost.
  • the refrigerant is then introduced through the four-way valve 3 from the accumulator 8 again into the compressor 1 and is again compressed by the compressor 1 to high temperature and high pressure gas which is then introduced through the bypass tube 21 into the outdoor side heat exchanger 4.
  • the four-way valve 3 is switched to the state in which the outdoor side heat exchanger 4 is used as a condenser and the indoor side heat exchanger 7 is used as an evaporator, the refrigerant gas exhausted from the outdoor side heat exchanger 4 is introduced through the indoor side heat exchanger 7 into the compressor 1 in one cycle. Accordingly, the heating operation cannot be performed during the defrosting operation.
  • the two operations can be performed simultaneously since heating can be effected by utilizing the high temperature and high pressure refrigerant gas accumulated in the indoor side heat exchanger 7, the refrigerant heat in the indoor side heat exchanger 7 being utilized. Further, the defrosting operation can be executed without switching the four-way valve 3 in this embodiment.
  • the compressor 1 repeats starting and stopping operations in order to control the temperature in the room in heating operation.
  • defrosting of the evaporator can be effected by opening and closing of the second solenoid valve 22 in synchronism with the starting and stopping operations of the compressor 1, i.e. switching operation of the compressor 1 may be continued during defrosting.
  • the second solenoid valve 22 When the compressor 1 is stopped and valve 5 closed in the apparatus thus constructed, the second solenoid valve 22 will open, the outlet side refrigerant from the compressor 1 is accordingly introduced through the bypass tube 21 into the outdoor side heat exchanger 4, and the outlet side pressure of the compressor 1 is thus lowered to balance with the inlet side pressure. Accordingly, since there is no pressure difference between the inlet side and the outlet side of the compressor when the compressor 1 is restarted, the starting torque is low and the electric power consumption is thus reduced compared with the prior art apparatus. In addition, since the starting torque of the compressor 1 is low, the size and capacity of the compressor may be reduced advantageously.
  • the second solenoid valve 22 is operated to open when the compressor 1 is stopped and to close a predetermined time, in the heating mode, after the compressor 1 is started.
  • the second solenoid valve 22 thus operated feeds some of the refrigerant, instead of through the check valve 2 into the high pressure side, into the lower pressure side, and accordingly decreases the starting torque of the compressor 1.
  • the second solenoid valve 22 provided in the bypass passage 21 is opened a short predetermined time before a defrosting operation is started and closed before the expiry of a predetermined short time after completion of the defrosting operation performed in the heating mode.
  • the second solenoid valve 22 receives a control signal from a frost detector (not shown) provided at the outdoor side heat exchanger 4.
  • the second solenoid valve 22 thus constructed introduces rapidly the high temperature and high pressure refrigerant gas into the outdoor side heat exchanger 4 in the defrosting operation, the defrosting time is short.
  • the second solenoid valve 22 is closed before completion of the defrosting operation, the refrigerant in the outdoor side heat exchanger 4 is used until the defrosting operation is completed.
  • the function of the outdoor heat exchanger 4 as the evaporator is quickly recovered when the operating mode is subsequently switched to the normal mode.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Claims (7)

1. Luftklimatisierungssystem mit einem Kompressor (1), einem ersten Wärmeaustauscher (7), Expansionsmitteln (6) und einem zweiten Wärmeaustauscher (4) in Reihe miteinander verbunden; und Mitteln zum wiederholten Anfahren und Stillsetzen des Kompressors im Ansprechen auf ein Kaumtemperaturerfassungsmittel, gekennzeichnet durch Mittel (2,5) zum Abtrennen von Kühlmittel auf einer Hochdruckseite des Kompressors von Kühlmittel auf einer Niederdruckseite des Kompressors, wenn der Kompressor stillgesetzt wird, und Umlenkmittel (21,22) zum Führen von Kühlmittel zum Kompressor (1) zum zweiten Wärmeaustauscher (4), um den zweiten Wärmeaustauscher abzutauen, während ein Erwärmungsbetrieb mit dem ersten Wärmeaustauscher (7) fortgesetzt wird.
2. System nach Anspruch 1, dadurch gekennzeichnet, daß die Abtrennungsmittel ein zwischen dem Auslaß des Kompressors (1) und einem Einlaß des ersten Wärmeaustauschers (7) vorgesehenes Kontrollventil (2) und ein erstes, zwischen einem Auslaß des ersten Wärmeaustauschers (7) und einem Einlaß des zweiten Wärmeaustauschers (4) vorgesehenes Magnetventil enthalten, daß ein Abzweigrohr für Kühlmittel zwischen dem Auslaß des Kompressors (1) und dem Kontrollventil (2) vorgesehen ist, daß die Umlenkmittel ein zweites Magnetventil (22) und eine Umwegleitung (21) haben, um ein Ende des Abzweigrohrs mit dem Kühlmittelrohr zwischen dem ersten Magnetventil (5) und dem zweiten Wärmeaustauscher (4) über das zweite Magnetventil (22) in Verbindung zu bringen, und daß Mittel zum Schließen des ersten Magnetventils (5) und zum Öffnen des zweiten Magnetventils (22) beim Durchführen des Abtaubetriebs im Heizbetrieb vorgesehen sind.
3. System nach Anspruch 2, dadurch gekennzeichnet, daß Mittel zum Schließen des ersten Magnetventils (5), zum Öffnen des zweiten Magnetventils (22) beim Stillsetzen des Kompressors (1) im Erwärmungsbetrieb und zum Öffnen des ersten Magnetventils (5) und zum Schließen des zweiten Magnetventils (22) beim Anlaufen des Kompressors (1) vorgesehen sind.
4. System nach Anspruch 2, dadurch gekennzeichnet, daß Mittel zum Schließen des ersten Magnetventils (5) und zum Öffnen des zweiten Magnetventils (22) beim Stillsetzen des Kompressors (1), zum Öffnen des ersten Magnetventils (5) beim Anlaufen des Kompressors und zum Schließen des zweiten Magnetventils (22) eine vorbestimmte Zeit nach dem Anlaufen des Kompressors (1) vorgesehen sind.
5. System nach Anspruch 2, dadurch gekennzeichnet, daß Mittel betreibbar während der Durchführung eines Abtaubetriebes in einem Heizbetrieb vorgesehen sind zum Öffnen des zweiten Magnetventils (22), zum Schließen des ersten Magnetventils (5) eine vorbestimmte Zeit nach dem Öffnen des zweiten Magnetventils (22), zum Schließen des zweiten Magnetventils (22) eine vorbestimmte Zeit vor Beendigung des Abtaubetriebes und zum Öffnen des ersten Ventils (5), wenn der Abtaubetrieb beendet ist.
6. System nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß der erste Wärmeaustauscher (7) ein Innenraumseiten-Wärmeaustauscher und der zweite Wärmeaustauscher (4) ein Freiluftseiten-Wärmeaustauscher ist.
7. System nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß der erste und zweite Wärmeaustauscher als Kondensator und Verdampfer betreibbar sind und ein Umkehrventil (3) zum Umkehren der Richtung des Kühlmittelflusses durch die Wärmeaustauscher vorgesehen ist.
EP81108580A 1981-10-20 1981-10-20 Luftklimatisierungssystem Expired EP0077414B1 (de)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE8585100213T DE3177054D1 (en) 1981-10-20 1981-10-20 Refrigeration cycle apparatus
EP81108580A EP0077414B1 (de) 1981-10-20 1981-10-20 Luftklimatisierungssystem
DE8181108580T DE3175833D1 (en) 1981-10-20 1981-10-20 Air temperature conditioning system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP81108580A EP0077414B1 (de) 1981-10-20 1981-10-20 Luftklimatisierungssystem

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP85100213.9 Division-Into 1981-10-20
EP87109204.5 Division-Into 1981-10-20

Publications (2)

Publication Number Publication Date
EP0077414A1 EP0077414A1 (de) 1983-04-27
EP0077414B1 true EP0077414B1 (de) 1987-01-14

Family

ID=8187964

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81108580A Expired EP0077414B1 (de) 1981-10-20 1981-10-20 Luftklimatisierungssystem

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EP (1) EP0077414B1 (de)
DE (2) DE3177054D1 (de)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4750672A (en) * 1987-05-15 1988-06-14 Honeywell Inc. Minimizing off cycle losses of a refrigeration system in a heating mode
NL8701527A (nl) * 1987-06-30 1989-01-16 Philips Nv Koelsysteem.
US4966013A (en) * 1989-08-18 1990-10-30 Carrier Corporation Method and apparatus for preventing compressor failure due to loss of lubricant
US9418281B2 (en) 2013-12-30 2016-08-16 Google Inc. Segmentation of overwritten online handwriting input
CN112650315B (zh) * 2020-09-09 2021-11-05 江苏振宁半导体研究院有限公司 一种温控器的温控方法

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH188957A (de) * 1936-01-21 1937-01-31 Sulzer Ag Kompressionskältemaschine.
NL7414728A (nl) * 1973-11-16 1975-05-21 Frimair Sa Warmtewisselaar, in het bijzonder voor compressor warmtepompen.
US4017286A (en) * 1975-12-22 1977-04-12 Westinghouse Electric Corporation Heat pump suction line vent
DE2806381A1 (de) * 1978-02-15 1979-08-16 Kulmbacher Klimageraete Kaeltemittelkreislauf einer waermepumpe
US4286438A (en) * 1980-05-02 1981-09-01 Whirlpool Corporation Condition responsive liquid line valve for refrigeration appliance

Also Published As

Publication number Publication date
EP0077414A1 (de) 1983-04-27
DE3175833D1 (en) 1987-02-19
DE3177054D1 (en) 1989-06-22

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