EP0077414A1 - Luftklimatisierungssystem - Google Patents

Luftklimatisierungssystem Download PDF

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Publication number
EP0077414A1
EP0077414A1 EP81108580A EP81108580A EP0077414A1 EP 0077414 A1 EP0077414 A1 EP 0077414A1 EP 81108580 A EP81108580 A EP 81108580A EP 81108580 A EP81108580 A EP 81108580A EP 0077414 A1 EP0077414 A1 EP 0077414A1
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EP
European Patent Office
Prior art keywords
compressor
valve
outlet
refrigerant
condenser
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
EP81108580A
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English (en)
French (fr)
Other versions
EP0077414B1 (de
Inventor
Fumio C/O Mitsubischi Denki K. K. Matsuoka
Hitoshi C/O Mitsubischi Denki K. K. Iijima
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.)
OFFERTA DI LICENZA AL PUBBLICO
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Mitsubishi Electric 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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to EP81108580A priority Critical patent/EP0077414B1/de
Priority to DE8585100213T priority patent/DE3177054D1/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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    • 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 a novel refigerant cycle apparatus which reduces the loss of energy produced at the time of starting and stopping the apparatus and which provides a highly efficient operation when operated repeatedly for starting and stopping the operation of an air conditioner or a refrigerator.
  • the invention relates to a novel air conditioning system which employs this refrigeration cycle apparatus and in which a continuous heating operation can be continuously carried out while performing defrosting of an outdoor heat exchanger.
  • a 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.
  • 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 refrigeraion cycle apparatus When the above-described refrigeraion cycle apparatus is used in an air conditioning system capable of operating in both cooling and heating modes and the air conditioning system is operated in the heating mode, the refrigerant must be made to flow in the reverse direction to perform defrosting.
  • an outdoor side heat exchanger is used as a condenser and an indoor side heat exchanger is operated as an evaporator. Accordingly, the heating operation of the side heat exchanger must be stopped during defrosting or a heater must be additionally provided.
  • a primary object of the invention is to provide.a refigeration cycle apparatus which can be repeatedly started and stopped and is of a type including a series connection of a compressor, a condenser, an expansion device and an evaporator.
  • 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 short time after the compressor is re-started.
  • a further object of the invention is to provide a novel air conditioning system which incorporates a series connection of a compressor, a condenser, an expansion device and an.evaporator, in which the refrigrant flow is stopped in an indoor side heat exchanger but in which the refrigerant is used in an outdoor heat exchanger while continuing a heating operation.
  • Another object of the invention is to provide a novel switching element used for the refrigeration cycle apparatus which utilizes a diaphragm opening or closing in accordance with the pressure difference between the two refrigerant pressures in the refrigeration cycle corresponding to the temperature of the refrigerant.
  • Still another object of this invention is to provide a refrigeration cycle apparatus in which, when it is used as an air conditioning system, evaporation of drain water condensed 6n the evaporator and return thereof into a room to be cooled are substantially eliminated by delaying the starting and stopping operations of the evaporator fan with respect to the starting and stopping operations of the compressor, respectively.
  • a refrigeration cycle apparatus including a compressor, a condenser, expansion means and an evaporator connected in series with each other. Means is provided for repeatedly starting and stopping the compressor. Further, means is also included for isolating refrigerant on a high pressure side of the compressor from refrigerant on the low pressure side of the compressor when the compressor is stopped.
  • the expansion means is an expansion valve and the isolating means is a check valve provided between an outlet of the compressor and an inlet of the condenser with a switching element being coupled between an outlet of the condenser and an inlet of the evaporator which is adaped to close upon stopping of the compressor and to open when the compressor is started.
  • a solenoid valve may be provided for the switching element.
  • the apparatus means include a thermal-valve heat sensitive tube provided between an outlet of the evaporator and the inlet of the compressor for controlling superheating of outlet refrigerant gas from the evaporator with the expansion valve.
  • the expansion valve is of a type having no bleed port.
  • the expansion means may be implemented with a capillary tube.
  • 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 4.
  • the refrigerant dissipates heat in the condenser 4 and is condensed to a high temperature and high pressure liquid.
  • the refrigerant liquid, increased in temperature and pressure by the condenser 4, is passed through a solenoid valve 5, which acts as a switching valve, and an expansion valve 6 where the refrigerant becomes a low temperature, low pressure liquid and from there is introduced into an evaporator 7.
  • the low temperature. and low pressure refrigerant liquid in the evaporator 7 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 7 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 repeats the refrigeration cycle.
  • Reference numeral 9 illustrates a fan for the condenser 4 and 10 a fan for the evaporator 7.
  • the four-way valve 3 is a change-over or switching valve which operates so that the condenser 4 can be used as an evaporator and the evaporator 7 used as a condenser.
  • the evaporator 7 is used as an indoor side heat exchanger, and the condenser 4 is used as an outdoor side heat exchanger.
  • the apparatus In the cooling mode, the apparatus is operated in a refrigeration cycle which in the heating mode the four-way valve 3 is switched so that the indoor side heat exchanger is used as a condenser and the outdoor side heat exchanger is used as an evaporator.
  • An air 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 interlocks 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 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.
  • the conventional refrigerant cycle incorporating not 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.
  • thermo-valve heat sensitive tube 11 which is filled with a gas whose pressure varies with temperature and detects the refrigerant gas temperature at the outlet of the evaporator 7 for controlling the refrigerant flow rate through the expansion valve 6.
  • Other components of the appa- - ratus are constructed in the same manner as in the first embodiment shown in Fig. 1.
  • FIG. 3 An expansion valve 6 is depicted in Fig. 3 of a type which may be used for the refrigeration cycle apparatus of the invention.
  • this expansion valve 6 is used as a superheating control device for the refrigerant gas from the evaporator 7, an additional advantageous effect is obtained in addition to those provided by the embodiment of Fig. 1. That is, the refrigerant within the evaporator 7 can be utilized more effectively, particularly, in the coo1ing mode operation of the apparatus.
  • thermo-valve heat sensitive tube 11 is not limited to the position shown in Fig. 2 but may also be disposed at any position from the output of the evaporator 7 to the inlet of the compressor 1.
  • thermo-valve heat sensitive tube 11 is not disposed between the evaporator 7 and the compressor 1 but is provided between the condenser 4 and the solenoid valve 5 for controlling the refrigerant flow rate of the expansion valve 6.
  • the refrigerant in the condenser may be effectively used to improve the efficiency of the apparatus when the condenser 4 is used as the indoor side heat exchanger in the heating mode.
  • Fig. 4 shows another example of an expansion valve 6 which may be used in the embodiment shown in Fig. 2.
  • This valve 6 has no bleed port 6a, which is different from the valve shown in Fig. 3, but the other components and parts are constructed in the same manner as those of the valve shown in Fig. 3.
  • the thermo-valve heat sensitive tube 11 used for controlling the expansion valve 6 is constructed in the same manner as that shown in Fig. 2 arid is positioned to detect the temperature of the outlet refrigerant gas of the evaporator 7.
  • thermo-valve heat sensitive tube 11 can be disposed at any position between the outlet of the evaporator 7 and the inlet of the compressor 1 in the same manner as in the embodiment shown in Fig. 2.
  • thermo-valve heat sensitive tube 11 is disposed at the outlet side of the condenser 4 but not between the evaporator 7 and the compressor 1 and the valve 6 is used as a supercooling control device for refrigerant gas of the outlet of the condenser 4, the refrigerant in the condenser 4 is effectively utilized to improve the efficiency of the apparatus when the condenser 4 is used as the indoor side heat exchanger.
  • FIG. 5 shows a further preferred embodiment of the refrigeration cyctem apparatus constructed according to the invention in which capillary tubes 12 and 13 are used instead of the expansion valve 6 of the first embodiment shown in Fig. 1 and a switching element 14 is provided instead of the solenoid valve 5 between the capillary tubes 12 and 13.
  • This switching element 14 is constructed to close when the compressor 1 is stopped and to open when the compressor 1 is started in the same manner as the solenoid valve 5 of the embodiment shown in Fig. 1.
  • the check valve 15 is provided.to effectively alter the length of the capillary tube since the apparatus will operate more efficiently if the expansion coefficient of the refrigerant is varied between the cooling mode and the heating mode in such a manner that the capillary tube is effectively increased in length in the heating mode.
  • the apparatus can be inexpensively constructed, even if the check valve 15 is added and can be operated similarly to the embodiment shown in Fig. 1 with the same advantageous effects.
  • the switching element 14 is constructed to compare the pressure P 2 , determined by the output side refrigerant gas temperature of the evaporator 7 as detected by the heat sensitive tube 11 provided between the outlet of the evaporator 7 and the inlet of the compressor 1, with the pressure P 1 of the refrigerant exhausted from the capillary tube 12, and to open when P 2 > P 1 and to close when P 2 ⁇ P 1 , in the same manner as described above.
  • an on-off element 16 is provided instead of the electromagnetic valve in Fig. 2.
  • the element 16 is on-off controlled by the temperature sensitive tube 11 provided on the output side of the evaporator 7.
  • Fig. 7 shows in cross section the element 16.
  • the on-off element 16 is automatically on-off controlled by the starting and stopping of the operation of the compressor 1 as mentioned above, the necessity of providing of means such as the electromagnetic valve 5 for detecting the starting and stopping of compressor 1 and means for converting this into election signals is eliminated.
  • the pressure corresponding to the temperature of the refrigerant detected by the heat sensitive tube 11 used to actuate the diaphragm of the on-off element 16 may be derived from the temperature of the refrigerant at the outlet of the condenser 4.
  • Fig. 8 illustrates still another preferred embodiment of an apparatus constructed according to the invention in which there are provided a refrigerant bypass tube 17 which connects the exhaust side of the compressor 1 with the inlet side of the compressor 1 and a switching element 20 disposed in the bypass tube 17 and which opens or close in response to signals from a detector 18 which senses the pressure of high pressure side refrigerant of the condenser 4 and a detector 19 which senses the exhaust pressure before the check valve 2.
  • the switching element 20 is fully closed when the exhaust refigerant pressure of the compressor 1 is higher than the high pressure side refrigerant pressure of the condenser 4 and fully open when the exhaust refrigerant pressure of the compressor 1 is lower than the high pressure side pressure of the condenser 4.
  • the other components and parts in this embodiment shown in Fig. 8 are constructed in the same manner as those of the embodiment shown in 'Fig. 1.
  • the solenoid valve 5 is opened when the compressor 1 is operated.
  • the switching element 20 is then closed since the exhaust refrigerant pressure of the compressor 1 is higher than the high pressure side refrigerant pressure of the condenser 4 so that the apparatus operates according to an ordinary refrigeration cycle. Since the solenoid valve is closed when the compressor 1 is stopped, the high pressure side refrigerant is isolated advantageously from the lower pressure side refrigerant during the refrigeration cycle.
  • the switching element 20 When the compressor 1 is stopped and the exhaust refrigerant pressure of the compressor 1 becomes lower than the high pressure side refrigerant pressure of the condenser 4, the switching element 20 fully opens to introduce the exhaust side refrigerant of the compressor 1 through the refrigerant bypass tube 17 to the intake side of the compressor 1 so as to thus balance the exhaust side pressure of the compressor 1 with the intake side pressure of the compressor 1. Because the distance between the exhaust side of the compressor 1 and the check valve 2 is short and the gas capacity of the refrigerant therebetween is small, the exhaust side of the compressor 1 is at a low pressure. Therefore, starting torque of the compressor 1 is low and the electric power consumption of the compressor during starting is correspondingly low.
  • the switching element 20 is not limited to the construction as described heretoforce. It also may be implemented with a solenoid valve or other switching element which can open and close in synchronization with the starting or stopping operation of the compressor 1. This embodiment provides the same advantages as those of the embodiment shown'in Fig. 8.
  • reference numeral 20a indicates an L-shaped casing, 20b a fluid passage extending longitudinally in the casing 20a, 20c an inlet, 20d an outlet.
  • the passage 20b has a narrow portion extending as a step from the major part of the passage.
  • Reference numeral 20e indicates a valve ball provided at the bent portion of the passage 20b with which the passage 20b'is opened and closed upon movement thereof.
  • Reference numeral 20f depicts a pad making contact with the ball 20e, 20g is a spring making contact at one end with the pad 20f.
  • 20h is a diaphragm housing provided at the top of the casing 20a
  • 20i is a segmented diaphragm which divides the housing 20h into two chambers.
  • a pad 20j is in contact with the lower surface of the diaphragm 20i.
  • Reference numeral 20k is a connecting pin which connects the pad 20j with the pad 20f
  • 201 is a fluid inlet provided at the top of the housing 20h into which a comparison pressure is introduced.
  • the tension of the spring 20g is suitably determined.
  • the fluid pressure introduced from the inlet 20c acts on the pad 20f which urges up the diaphragm 20i through the connecting pin 20k and the pad 20j.
  • the switching element 20 opens when the comparison fluid pressure is higher than the sum of the fluid pressure from the current element inlet 20c and the equivalent pressure provided by the tension of the spring 20g and closes when the comparison.pressure is, on the contrary, lower than that sum.
  • the switching element 20 is provided midway of the tube 17 in the embodiment shown in Fig. 8 and the comparison fluid employed is the high pressure side refrigerant of the condenser 4, that is, when the inlet 20l of the diaphragm housing 20h is connected to the branch tube extending from the high pressure side refrigerant tube of the condenser 4, the apparatus operates in the same manner as the embodiment shown in Fig. 8.
  • thermo-valve heat sensitive tube 11 shown between the outlet of the evaporator 4 and the inlet of the compressor 1 is connected to the inlet 20t for the comparison fluid in the chamber on the top of the diaphragm housing 20h.
  • the thermo-valve heat sensitive tube 11 is filled with a gas the pressure of which varies in response to the sensed temperature thereof.
  • the components and parts of this element are constructed in the same manner as the switching element 20 shown in Fig. 9.
  • thermo-valve heat sensitive tube 11 thus constructed varies the internal pressure, that is, the pressure acting on the top of the diaphragm in response to the output side refrigerant gas temperature of.the evaporator.
  • the switching element 14 controls the flow rate of the refrigerant gas exhausted from the capillary tube 12 into the inlet 20c of the switching element 14.
  • the refrigerant gas pressure is applied to the pad 20f.
  • the pressure p 1 of the refrigerant gas exhausted from the capillary tube 12 is lower than the pressure P 2 which is determined according to the outlet refrigerant gas temperature of refrigerant from the evaporator 7 and hence the pressure P 2 is higher than the sum of the pressure P 1 and the tension equivalent pressure AP of the spring. That is, P 2 > P 1 + ⁇ P. Accordingly, the valve ball 20e is in its lower position which causes the switching element 14 to be opened. A refrigeration cycle can then be performed.
  • the compressor 1 Since the output side refrigerant gas from the capillary tube 12 is, when the compressor 1 is stopped, not absorbed by the compressor 1, the refrigerant pressure P 1 is increased while the pressure P 2 corresponding to the output refrigerant gas temperature of the evaporator 7 is not substantially increased. Consequently, the pressure P 1 + ⁇ P becomes higher than P 21 i.e., P 2 ⁇ P 1 + AP. Therefore, the valve ball 20e is accordingly raised and the switching element 14 is thus closed. Therefore, when the compressor 1 is stopped, the high pressure side refrigerant of the refrigeration cycle is isolated from the low pressure side refrigerant.
  • Fig. 11 shows still another embodiment of the apparatus constructed according to the invention in which there is provided a controller 23 which starts operation when power to the compressor 1 is cut off.
  • the controller 23 stops the operation of a fan 10 for an evaporator 7 approximately one minute after the controller 23 is activated and operates the fan 10 for the evaporator 7 for several seconds when power to the compressor 1 is turned on.
  • the other components and parts of this apparatus shown in Fig. 11 are constructed in the same manner as those of the embodiment shown in Fig. 1.
  • the controller 23 is composed of a flip-flop 25 receiving an output signal from a detector 24 for detecting the driving condition of the compressor 1, a At timer 26 adapted to be set in response to an inverted output signal of the flip-flop 25, a At2 timer 27 adapted to be set in response to a non-inverted output signal of the flip-flop 25, and a flip-flop 28 receiving outputs from the timers 26 and 27 to produce an instruction signal for driving or stopping of the fan 10 of the evaporator 7.
  • the flip-flop 25 Upon reception a stop instruction signal of the compressor 1 from the detector 24, the flip-flop 25 operates to produce an inverted output signal to the timer 26 to set the timer 26. Then the timer 26 operates to produce an output signal to the flip-flop circuit 28 after a predetermined time has passed, one minute for instance in this embodiment, so that the flip-flop 28 is reset to produce a driving stop instruction signal. As a result, the fan 10 of the evaporator 7 is stopped. The output signal of the timer 26 is fed back to its reset terminal as a reset signal to the timer 26.
  • the flip-flop 25 when the flip-flop 25 receives, driving instruction signal for the compressor 1 from the detector 24, the flip-flop 25 produces an output to set the timer 27. After a predetermined period of time, five seconds for instance, the timer 27 operates to produce an output to set the flip-flop 28. The flip-flop 28 produces a driving instruction signal to thereby start driving of the : fan 10. Similar to the above operation, the output signal of the timer 27 is fed back to the reset terminal of the timer 27 to reset the timer 27.
  • the fan 10 starts its operation when the temperature of the evaporator 7 is sufficiently low during the operation of the compressor 1, the drain water is not evaporated again. 'Therefore, it is possible to maintain the humidity in the room to be air conditioned at a much lower level than is possible with the conventional apparatus.
  • Fig. 12 shows a modification of the embodiment shown in Fig. 1, using the latter as an air conditioning system in the cooling mode.
  • the four-way valve 3 is . turned to connect the condenser 4 as an outdoor heat exchanger and the evaporator 7 as an indoor heat exchanger.
  • 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 in addition to the components and parts in the embodiment shown in Fig. 1.
  • the second selonoid 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 heat exchanger in the heating mode.
  • the second solenoid valve 22 provided in the bypass passage 21 is closed in the heating mode, 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 low temperature refrigerand 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, in the same manner as in the embodiment shown in Fig. 1, to thus isolate the high pressure side refrigerant and the lower pressure side refrigerant. Accodingly, the COP of the compressor 1 is improved.
  • the solenoid valve 5 is closed by a defrost operation command signal while simultaneously the second solenoid valve 22 in the bypass passage 21 is opened. Accordingly, the high temperature and high pressure refrigerant gas in the indoor side heat exchanger 7 is condensed 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 4 through 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 defrosting cycle in the defrosting cycle 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 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 can be 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.
  • the opening and closing of the second solenoid valve 22 is synchronized with the starting and stopping operations of the compressor 1.
  • the defrosting operation can also be conducted in the same manner as that executed in the above embodiment.
  • the second solenoid valve 22 When the compressor 1 is stopped 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 does not feed the refrigerant compressed through the check valve 2 into the high pressure side but passes it into the lower pressure side, and accordingly decreases the starting torque of the compressor 1.
  • the second solenoid valve 21 provided in the bypass passage 21 is opened a short predetermined time before a defrosting operation is started and closed before a predetermined short time after completion of the defrosting operation in a 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 heating 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)
EP81108580A 1981-10-20 1981-10-20 Luftklimatisierungssystem Expired EP0077414B1 (de)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP81108580A EP0077414B1 (de) 1981-10-20 1981-10-20 Luftklimatisierungssystem
DE8585100213T DE3177054D1 (en) 1981-10-20 1981-10-20 Refrigeration cycle apparatus
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 true EP0077414A1 (de) 1983-04-27
EP0077414B1 EP0077414B1 (de) 1987-01-14

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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)

Cited By (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
EP0297656A1 (de) * 1987-06-30 1989-01-04 Whirlpool International B.V. Kühlsystem
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
CN112650315A (zh) * 2020-09-09 2021-04-13 江苏振宁半导体研究院有限公司 一种温控器的温控方法

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* 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.
DE2335383A1 (de) * 1973-07-12 1975-02-06 Danfoss As Thermostatisches expansionsventil
DE2453899A1 (de) * 1973-11-16 1975-05-28 Frimair Sa Waermeaustauscher, insbesondere fuer waermepumpen mit verdichter
US4017286A (en) * 1975-12-22 1977-04-12 Westinghouse Electric Corporation Heat pump suction line vent
EP0003578A2 (de) * 1978-02-15 1979-08-22 KKW Kulmbacher Klimageräte-Werk GmbH Kältemittelkreislauf einer Wärmepumpe
US4286438A (en) * 1980-05-02 1981-09-01 Whirlpool Corporation Condition responsive liquid line valve for refrigeration appliance

Patent Citations (6)

* 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.
DE2335383A1 (de) * 1973-07-12 1975-02-06 Danfoss As Thermostatisches expansionsventil
DE2453899A1 (de) * 1973-11-16 1975-05-28 Frimair Sa Waermeaustauscher, insbesondere fuer waermepumpen mit verdichter
US4017286A (en) * 1975-12-22 1977-04-12 Westinghouse Electric Corporation Heat pump suction line vent
EP0003578A2 (de) * 1978-02-15 1979-08-22 KKW Kulmbacher Klimageräte-Werk GmbH Kältemittelkreislauf einer Wärmepumpe
US4286438A (en) * 1980-05-02 1981-09-01 Whirlpool Corporation Condition responsive liquid line valve for refrigeration appliance

Cited By (7)

* 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
EP0297656A1 (de) * 1987-06-30 1989-01-04 Whirlpool International B.V. Kühlsystem
US4966013A (en) * 1989-08-18 1990-10-30 Carrier Corporation Method and apparatus for preventing compressor failure due to loss of lubricant
FR2651034A1 (fr) * 1989-08-18 1991-02-22 Carrier Corp Procede et dispositif pour empecher une panne de compresseur due a une perte de lubrifiant
US9418281B2 (en) 2013-12-30 2016-08-16 Google Inc. Segmentation of overwritten online handwriting input
CN112650315A (zh) * 2020-09-09 2021-04-13 江苏振宁半导体研究院有限公司 一种温控器的温控方法
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

Also Published As

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EP0077414B1 (de) 1987-01-14
DE3177054D1 (en) 1989-06-22
DE3175833D1 (en) 1987-02-19

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