EP0779481A2 - Système à circuit frigorifique - Google Patents

Système à circuit frigorifique Download PDF

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Publication number
EP0779481A2
EP0779481A2 EP96119908A EP96119908A EP0779481A2 EP 0779481 A2 EP0779481 A2 EP 0779481A2 EP 96119908 A EP96119908 A EP 96119908A EP 96119908 A EP96119908 A EP 96119908A EP 0779481 A2 EP0779481 A2 EP 0779481A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
condenser
passage
evaporator
compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP96119908A
Other languages
German (de)
English (en)
Other versions
EP0779481A3 (fr
Inventor
Junpei c/o Showa Aluminum Corporation Nakamura
Keiji c/o Showa Aluminum Corporation Yamazaki
Yutaka c/o Showa Aluminum Corporation Higo
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.)
Showa Aluminum Can Corp
Original Assignee
Showa Aluminum 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 Showa Aluminum Corp filed Critical Showa Aluminum Corp
Publication of EP0779481A2 publication Critical patent/EP0779481A2/fr
Publication of EP0779481A3 publication Critical patent/EP0779481A3/fr
Withdrawn legal-status Critical Current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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/063—Feed forward expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/051—Compression system with heat exchange between particular parts of the system between the accumulator and another part of the 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series

Definitions

  • This invention relates to a refrigeration cycle system for use in a refrigeration device such as an automobile air conditioner, a room air conditioner, or the like.
  • FIG. 14 A conventional refrigeration cycle system is shown in FIG. 14.
  • the refrigeration cycle system comprises a compressor 51, a condenser 53 connected to the compressor 51 at the refrigerant output side thereof by way of a refrigerant passage 52 and an evaporator 55 connected to the compressor 51 at the refrigerant input side thereof by way of a refrigerant passage 54.
  • the output side of the condenser 53 and the input side of the evaporator 55 are connected by refrigerant passages 57, 59 and an expansion valve 56, or a capillary tube, or the like, as a decompression means intervening therebetween.
  • this refrigeration cycle system as indicated by arrows in FIG. 14, the following cycle is repeated.
  • a high pressure and high temperature gaseous refrigerant from the compressor 51 is condensed in the condenser 53 to become a high pressure and high temperature liquid refrigerant.
  • the high pressure and high temperature liquid refrigerant is passed through the expansion valve 56 to become a low pressure and low temperature liquid refrigerant.
  • the low pressure and low temperature liquid refrigerant is evaporated in the evaporator 55 to become a low pressure and low temperature gaseous refrigerant.
  • the low pressure and low temperature gaseous refrigerant is returned to the compressor 51.
  • the above mentioned conventional refrigeration cycle system is designed to superheat the refrigerant so as to increase the refrigeration effect and thus improve the performance of the refrigeration cycle.
  • the evaporator 55 is designed to have a superheating portion in the refrigerant passage near the outlet such that almost only gasified refrigerant passes through the superheating portion. Therefore, a liquid refrigerant is prevented from returning to the compressor 51 from the evaporator 55.
  • the above mentioned conventional refrigeration cycle system is also designed to supercool (subcool) the refrigerant so as to improve the performance of the refrigeration cycle.
  • the condenser 53 is designed to have a supercooling portion (subcooling portion) in the refrigerant passage near the outlet such that only liquefied refrigerant passes through the supercooling portion.
  • providing a superheating portion in the evaporator 55 means providing a flow area for a gasified refrigerant in the evaporator 55. Therefore, in the evaporator 55, refrigerant flowing through a refrigerant flow area, except for the superheating portion, is in a liquid state or in a sprayed state. The refrigerant which is in a liquid state or sprayed state will be gasified, thereby increasing the heat transfer rate. However, the refrigerant flowing through the superheating portion is already in a gasified state, thus the heat transfer rate in the superheating portion is low. As a result, when observed as a whole, the heat transfer rate between the refrigerant and the evaporator 55 is decreased and thus the heat exchange performance of the evaporator 55 is low.
  • an evaporator which is superheated is inferior in heat exchange performance as compared to an evaporator having no superheating, provided that both evaporators are the same in size.
  • the evaporator having superheating must be larger in size than the evaporator having no superheating because the evaporator having superheating has a superheating portion.
  • the pressure loss of the refrigerant passing through the evaporator 55 is larger than that of the refrigerant passing through an evaporator having no superheating, thereby increasing the pressure loss of the refrigerant in the whole refrigerant cycle.
  • the refrigerant passing through the superheating portion is in a gaseous state and has a large specific volume as compared to the refrigerant in a liquid state or in sprayed state (i.e., in a gas and liquid mixed state).
  • the specific volume in the superheating portion is large and because the refrigerant passages of the evaporator are narrow, the pressure loss of the refrigerant passing through the evaporator becomes larger.
  • an accumulator 60 may be provided within a refrigerant-passage connecting the evaporator 55 and the compressor 51 so as to decrease or delete the effect of the superheating portion of the evaporator 55.
  • the liquid refrigerant which remains unevaporated in the evaporator 55 will be captured by the accumulator 60.
  • the heat transfer ratio between the evaporator 55 and the refrigerant, i.e., the performance of the evaporator 55 can be improved.
  • the evaporator 55 can thus be smaller in size and the pressure loss of the refrigerant passing through the evaporator 55 can be decreased.
  • the accumulator 60 merely captures the liquid refrigerant which remains unevaporated in the evaporator 55.
  • the refrigeration cycle system can only have a small number of degrees of superheating, or even no degrees of superheating. As a result, the refrigeration effect will not be improved with such superheating.
  • the condenser 53 having a supercooling portion, the heat transfer rate between the refrigerant and the condenser 53 is decreased, which deteriorates the heat exchange performance thereof, as compared to a condenser having no supercooling portion therein.
  • providing a supercooling portion in the condenser 53 means providing a refrigerant flow area for a liquefied refrigerant in the condenser 53. Therefore, in the condenser 53 a refrigerant flowing through a refrigerant flow area, except for the supercooling portion, is in a gaseous state or in a sprayed state.
  • the refrigerant in a gaseous state or in a sprayed state proceeds to be liquefied, thereby increasing the heat transfer rate.
  • the refrigerant flowing through the supercooling portion is in a liquefied state, and thus the heat transfer rate in the supercooling portion deteriorates.
  • the heat transfer ratio between the refrigerant and the condenser 53 is decreased and thus the heat exchange performance of the condenser 53 deteriorates.
  • the condenser having such supercooling is inferior in heat exchange performance to a condenser having no supercooling, provided that both condensers are the same in size.
  • the condenser having supercooling in order to demonstrate the same heat exchange performance in both condensers, one having supercooling and the other not having supercooling, the condenser having supercooling must be larger in size than the condenser not having supercooling because of the supercooling portion.
  • the present invention overcomes, among other things, the problems mentioned above. It is an object of the invention to provide a refrigeration cycle system in which the superheating degree and the supercooling degree can effectively become large and thus achieve an enhancement in the refrigerant effects and an improvement in the performance of the refrigerant cycle.
  • a refrigerant cycle system comprises a refrigerant circulation circuit including a compressor, a condenser,an evaporator and a depressurizing means and a heat exchanging portion.
  • the heat exchanging portion exchanges heat between at least a portion of refrigerant flowing from the compressor to the depressurizing means and at least a portion of refrigerant flowing from the depressurizing means to the compressor.
  • the refrigerant cycle system includes a heat exchanging portion for exchanging heat between at least a portion of refrigerant flowing from the compressor to the depressurizing means and at least a portion of refrigerant flowing from the depressurizing means to the compressor. Therefore, the refrigerant returning to the compressor can be superheated and the refrigerant flowing toward the depressurizing means can be supercooled. As a result, the refrigerant effect can be increased and the performance as the refrigerant cycle can be improved.
  • each refrigerant is either superheated or supercooled by exchanging heat between a low temperature refrigerant and a high temperature refrigerant which are greatly different in temperature. Therefore, each refrigerant can be effectively superheated or supercooled and, thus, can greatly improve the performance of the refrigerant cycle as compared with a conventional refrigerant cycle in which each refrigerant is separately superheated or supercooled by air at room temperature.
  • the superheat portion in the evaporator can be decreased or omitted because the refrigerant returning to the compressor is superheated by exchanging heat in the heat exchanging portion. Therefore, the evaporator can be compact and superior in heat exchange performance, and thus the pressure loss of the refrigerant passing through the evaporator can be deceased.
  • the refrigerant flowing toward the expansion valve can be largely supercooled because the refrigerant is supercooled by exchanging heat in the heat exchanging portion. Therefore, the dry degree of the liquefied refrigerant passed through the expansion valve can be effectively lowered. Further, the pressure loss of the refrigerant passing through the evaporator can be effectively decreased. Furthermore, the heat exchanging performance of the evaporator can be effectively improved.
  • FIG. 1 illustrates a first embodiment of a refrigerant circuit of a refrigerant cycle system according to the present invention.
  • FIG. 2 is an inner side view of an accumulator equipped in the above refrigerant cycle system.
  • FIG. 3 illustrates a second embodiment of a refrigerant circuit of a refrigerant cycle system according to the present invention.
  • FIG. 4 illustrates a third embodiment of a refrigerant circuit of a refrigerant cycle system according to the present invention.
  • FIG. 5 illustrates a fourth embodiment of a refrigerant circuit of a refrigerant cycle system according to the present invention.
  • FIG. 6 is an inner side view of a heat exchanging portion integrating a liquid-receiver with an accumulator of the fourth embodiment.
  • FIG. 7 illustrates a filth embodiment of a refrigerant circuit of a refrigerant cycle system according to the present invention.
  • FIG. 8A and 8B illustrate a sixth embodiment of a refrigerant cycle system according to the present invention, wherein FIG. 8A illustrates a refrigerant circuit and FIG. 8B is an explanatory view of the heat exchanging portion.
  • FIG. 9 illustrates a seventh embodiment of a refrigerant circuit of a refrigerant cycle system according to the present invention.
  • FIG. 10A and 10B illustrate an evaporator and a heat exchanging portion of the seventh embodiment, wherein FIG. 10A is an inner front view thereof and FIG. 10B is an inner plan view thereof.
  • FIG. 11 illustrates an eighth embodiment of a refrigerant circuit of a refrigerant cycle system according to the present invention.
  • FIG. 12 illustrates a ninth embodiment of a refrigerant circuit of a refrigerant cycle system according to the present invention.
  • FIG. 13A and 13B illustrate a tenth embodiment of a refrigerant cycle system according to the present invention, wherein FIG. 13A illustrates a refrigerant circuit of the embodiment ad FIG. 13B is an explanatory inner view of a valve device.
  • FIG. 14 illustrates a refrigerant circuit of a conventional refrigerant cycle system.
  • FIG. 15 illustrates a refrigerant circuit equipped with an accumulator in the conventional refrigerant cycle system.
  • the numeral 1 denotes a compressor
  • the numeral 2 denotes a condenser
  • the numeral 3 denotes an evaporator
  • the numeral 4 denotes an expansion valve as a depressurizing means
  • the numeral 11 denotes a heat exchanging portion.
  • the condenser 2 is connected to the compressor 1 at the refrigerant output side thereof by way of refrigerant passages 5 (5a and 5b).
  • the evaporator 3 is connected to the compressor 1 at the refrigerant input side thereof by way of refrigerant passages 6 (6a and 6b).
  • the output side of the condenser 2 and the input side of the evaporator 3 are connected by refrigerant passages 10 (7 and 9) with an expansion valve 4 intervened therein to form a refrigerant circuit.
  • a decompression means a capillary tube, an orifice tube, or the like, may be used.
  • the heat exchanging portion 11 exchanges heat between the refrigerant passing through the refrigerant passage 5 connecting the compressor 1 to the evaporator 3 and the refrigerant passing through the refrigerant passage 6 connecting the evaporator 3 to the compressor 1.
  • an accumulator 12 is provided within the refrigerant passage 6 (6a and 6b) connecting the compressor 1 and the evaporator 3. This accumulator 12 is used as the heat exchanging portion 11 and exchanges heat between the refrigerant accumulated in the accumulator 12 and the refrigerant passing through the refrigerant passage 5 connecting the compressor 1 to the condenser 2.
  • the accumulator 12 is configured as shown in FIG. 2.
  • the accumulator 12 includes a liquid accumulating container 13 which is, at the upper portion, provided with a first refrigerant inlet port 14 and a first refrigerant outlet port 15.
  • the first refrigerant outlet port 15 is connected in fluid communication with one end of a pipe 16 extended into the container 13 with the other end of the pipe 16 opening proximate at the uppermost portion in the container 13, such that as the refrigerant is introduced in the container 13 through the first refrigerant inlet port 14, the liquid refrigerant can be accumulated in the lower portion of the container 13 and the gaseous refrigerant can be led to the outside through the pipe 16 and the first refrigerant outlet port 15.
  • the above mentioned construction of the accumulator 12 is similar to a conventional accumulator.
  • the container 13 is further provided with a second refrigerant inlet port 17 and a second refrigerant outlet port 19. Both the ports 17 and 19 are connected in fluid communication via a high heat conductance heat exchanging pipe 20 extending through the container 13 so that heat exchange between the refrigerant in the heat exchanging pipe 20 and the refrigerant accumulated in the container 13 can be achieved.
  • the first refrigerant inlet port 14 is connected to a pipe constituting the refrigerant passage 6b from the evaporator 3 and the first refrigerant outlet port 15 is connected to a pipe constituting the refrigerant passage 6a toward the compressor 1, and further the second refrigerant inlet port 17 is connected to a pipe constituting the refrigerant passage 5a from the compressor 1 and the second refrigerant outlet port 19 is connected to a pipe constituting the refrigerant passage 5b toward the condenser 2.
  • the accumulator 12 is built in the refrigerant cycle.
  • a low temperature refrigerant from the evaporator 3 is passed through the liquid accumulating container 13 of the accumulator 12 and then returned to the compressor 1.
  • a high temperature refrigerant from the compressor 1 is passed through the heat exchanging pipe 20 provided in the liquid accumulating container 13 of the accumulator 12 and then introduced to the condenser 2.
  • the low temperature refrigerant accumulated in the container 13 is heated by the high temperature refrigerant in the heat exchanging pipe 20. Therefore, the refrigerant returning to the compressor 1 is superheated and completely gasified.
  • the high temperature refrigerant in the heat exchanging pipe 20 is cooled by the low temperature refrigerant in the accumulating container 13.
  • the refrigerant sent to the expansion valve 4 is supercooled and completely liquefied.
  • the gaseous refrigerant returning to the compressor 1 can be superheated and the liquified refrigerant sent to the expansion valve 4 can be supercooled, in such a manner that the refrigerant effect is increased and the performance as the refrigerant cycle is improved.
  • each refrigerant is superheated or supercooled by exchanging heat between the low temperature refrigerant and the high temperature refrigerant which are greatly different in temperature. Therefore, each refrigerant can be effectively superheated or supercooled as compared to the conventional refrigerant cycle in which each refrigerant is superheated or supercooled by air at room temperature, thus the performance of the refrigerant cycle can be greatly improved.
  • the superheat portion in the evaporator 3 can be decreased or omitted because the refrigerant returning to the compressor 1 is superheated by exchanging heat in the heat exchanging portion 11. Therefore, the evaporator 3 can be compact and superior in heat exchange performance, and the pressure loss of the refrigerant passing through the evaporator 3 can be decreased.
  • the refrigerant sent to the expansion valve 4 can be largely supercooled because the refrigerant is supercooled by exchanging heat in the heat exchanging portion 11. Therefore, the dry degree of the liquefied refrigerant passed through the expansion valve 4 can be effectively lowered. Further, the pressure loss of the refrigerant passing through the evaporator 3 can be effectively decreased and the heat exchanging performance of the evaporator 3 can also be effectively improved.
  • the accumulator 12 is modified to include the heat exchanging portion 11 as mentioned above, a large refrigerating ability of the accumulator 12, not previously contemplated, can be effectively provided to supercool the refrigerant flowing toward the expansion valve 4, and thus energy can be effectively utilized. Further, the original gas-liquid separating function of the accumulator 12 can be improved and thus the liquid refrigerant is effectively prevented from returning to the compressor 1.
  • FIG. 3 illustrates a second embodiment of the refrigerant cycle system according to the present invention.
  • the heat exchanging portion 11 exchanges heat between the refrigerant passing through the refrigerant passage 7 (7a and 7b) connecting the condenser 2 to the expansion valve 4 and the refrigerant passing through the refrigerant passage 6 (6a and 6b) connecting the evaporator 3 to the compressor 1.
  • the accumulator 12 which has the same structure of the accumulator of the first embodiment and has the second refrigerant inlet port 17 connected to the pipe constituting the refrigerant passage 7a from the condenser 2 and has the second refrigerant outlet port 19 connected to the pipe constituting the refrigerant passage 7b toward the expansion valve 4.
  • the accumulator 12 is built in the refrigerant cycle.
  • the condenser 2 can be compact and superior in heat exchange performance.
  • the supercooling portion in the condenser 2 which passes through the liquefied refrigerant is decreased or omitted, the refrigerant from the condenser 2 is supercooled by passing through the heat exchanging portion 11.
  • the supercooling portion in the condenser 2 can be decreased or omitted. Therefore, the condenser 2 can be effectively compact and superior in its heat exchange performance.
  • the refrigerant condensing ability of the condenser 2 can be improved.
  • the condensing ability of the condenser 2 somewhat deteriorates because the refrigerant cooled in the heat exchanging portion 11 is subjected to be condensed in the condenser 2.
  • the condenser 2 can maintain high condensing ability thereof because the high temperature refrigerant from the compressor 1 is directly fed into the condenser 2 and condensed therein.
  • FIG. 4 illustrates a third embodiment of the refrigerant cycle system.
  • the heat exchanging portion 11 exchanges heat between the refrigerant passing through the refrigerant passage 7 (7a, 7b and 7C) connecting the condenser 2 to the expansion valve 4 and the refrigerant passing through the refrigerant passage 6 (6a and 6b) connecting the evaporator 3 to the compressor 1, and the accumulator 12 is used as a heat exchanging portion 11.
  • a liquid-receiver 32 is interposed in the refrigerant passage 7 (7c and 7a) connecting the condenser 2 to the expansion valve 4 so that the refrigerant from the condenser 2 exchanges heat in the heat exchanging portion 11 of the accumulator 12 after passing through the liquid-receiver 32 and then is send to the expansion valve 4.
  • alter the gaseous ingredient is removed from the refrigerant in the liquid-receiver 32, only the liquefied refrigerant is send to the accumulator 12 and then exchanges heat to be supercooled.
  • the refrigerant flowing to the expansion valve 4 can be effectively supercooled in comparison with the case in which the liquefied refrigerant containing gaseous refrigerant exchanges heat in the heat exchanging portion 11.
  • FIG. 5 illustrates a fourth embodiment of the refrigerant cycle system.
  • an accumulator and a liquid-receiver are integrated to form a heat exchanging portion 11.
  • the heat exchanging portion 11 includes a container 39 which is divided by a dividing wall 36 into an accumulator cell 12 and a liquid-receiving cell 32.
  • the dividing wall 36 is equipped with fins 37 for promoting heat exchange between the accumulator cell 12 and the liquid-receiving cell 32.
  • the refrigerant passages 7a and 7b connecting the condenser 2 to the expansion valve 4 are connected to the liquid-receiving cell 32.
  • the refrigerant passages 6a and 6b connecting the evaporator 3 to the compressor 1 are connected to the accumulator cell 12.
  • a large quantity of a high temperature refrigerant and a low temperature refrigerant can very effectively exchange heat in the heat exchanging portion 11.
  • FIG. 7 illustrates a filth embodiment of the refrigerant cycle system according to the present invention.
  • This system is similar to the first embodiment but different from the first embodiment in that the heat exchanging portion 11 is not composed of an accumulator but of a heat exchange piping system in which heat exchanging is performed between heat exchange piping portions 27 and 29.
  • the heat exchanging portion 11 is not necessarily composed from an accumulator, this same concept can be applied to the second embodiment.
  • FIG. 8A illustrates a sixth embodiment of the refrigerant cycle system according to the present invention.
  • the refrigerant passage 5 connecting the compressor 1 to the condenser 2 and the refrigerant passage 7 connecting the condenser 2 to the expansion valve 4 are bypassed by the bypass refrigerant passages 30, 30.
  • the numeral 11 denotes a heat exchanging portion. The heat exchanging portion 11 exchanges heat between the refrigerant passing through the bypass refrigerant passage 30 and the refrigerant passing through the inner passage of the outlet side of the evaporator 3.
  • This heat exchanging portion 11 is, for example, constructed as follows. As shown in FIG. 8B, the heat exchanging portion 11 includes a final refrigerant passage 3b of the evaporator 3 connected to the outlet 3a, and an independent heat exchanging passage 31 adjacent to the final refrigerant passage 3b. In this heat exchanging portion 11, the heat exchanging passage 31 is interposed in fluid communication in the above mentioned bypass refrigerant passage 30. A liquid-receiver 32 is interposed in the refrigerant passage 7 between a position down stream of the juncture of the bypass refrigerant passage 30 and the refrigerant passage 7 and a position up stream from the expansion valve 4.
  • the high temperature refrigerant advancing toward the condenser 2 is divided into two refrigerant flow paths, a refrigerant flow path into the condenser 2 and a refrigerant flow path into the bypass passage 30.
  • the low temperature refrigerant passing through the final refrigerant passage 3b of the evaporator 3 is heated and the refrigerant is progressively superheated.
  • the high temperature refrigerant passing through the bypass passage 30 is cooled.
  • the refrigerant After passing through the bypass passage 30, the refrigerant is merged with the refrigerant passed through the condenser 2, thereby enhancing the supercooling degree of the liquid refrigerant sent to the expansion valve 4.
  • alter the merging by passing through the liquid-receiver 32, the refrigerant passed through the bypass passage 30 and the refrigerant passed through the condenser 2 are mixed.
  • the supercooling degree of the liquid refrigerant flowing toward the expansion valve 4 is effectively enhanced.
  • the low temperature refrigerant passing through the final refrigerant passage 3b of the evaporator 3 is compulsively heated by the high temperature refrigerant as mentioned above.
  • a sufficient superheat degree can be achieved and the superheating portion of the evaporator 3 can be effectively decreased. Therefore, the evaporator 3 can be small in size and can be enhanced in its heat exchanging performance.
  • the pressure loss of the refrigerant in the evaporator 3 can be decreased. Furthermore, the pressure loss of the refrigerant passing through the circuit can be decreased because an accumulator can be omitted.
  • FIG. 9 illustrates a seventh embodiment of the refrigerant cycle system according to the present invention.
  • a heat exchanging portion 11 is equipped at the condenser 2.
  • this condenser 2 is so-called multi-flow or parallel-flow type heat exchanger having a plurality of tubes 41 whose ends are connected in fluid communication to a cylindrical hollow header 42.
  • the numeral 43 denotes a fin.
  • the inside of the vertically disposed header 42 is divided by a dividing wall 44 having a high thermal conductivity into two chambers 45, 46.
  • the chamber 45 is connected to the tubes 41, and the chamber 46 is not connected to the tubes 41.
  • the chamber 45 connected to the tubes 41, as an essential part of the condenser, is connected to the refrigerant passages 7 toward the expansion valve 4.
  • the chamber 46 not connected to the tubes 41, which functions as a part of an accumulator, is connected to the refrigerant passages 6a, 6b connecting the evaporator 3 to the compressor 1.
  • the high temperature refrigerant condensed in the tubes 41 is introduced into the chamber 45 of the header 42 connected to the tubes 41 and the low temperature refrigerant evaporated in the evaporator 3 is introduced into the chamber 46 of the header 42 not connected to the tubes 41.
  • Both the refrigerants exchange heat through the dividing wall 44 such that the refrigerant toward the compressor 1 is superheated and the refrigerant toward the expansion valve 4 is supercooled.
  • an liquid-receiver may be interposed in a refrigerant passage 7 connecting the condenser 2 to the expansion valve 4.
  • FIG. 11 illustrates an eighth embodiment of the refrigerant cycle system according to the present invention.
  • This refrigerant cycle system is especially useful for an automobile air conditioning system.
  • a bypass passage 22 22a and 22b
  • a heat exchanging portion 11 is provided so as to exchange heat between the refrigerant passing through the bypass passage 22 and the refrigerant passing through the refrigerant passage 6 connecting the evaporator 3 to the compressor 1.
  • an accumulator 12 having the same structure of the accumulator in the first embodiment is used.
  • the second refrigerant inlet port 17 is connected to the pipe constituting the bypass passage 22a from the compressor 1 and the second refrigerant outlet port 19 is connected to the pipe constituting the bypass passage 22b toward condenser 2.
  • the refrigerant inlet end portion of the bypass passage 22 is connected to the refrigerant passage 5 connecting the compressor 1 to the condenser 2 by way of a distributor 23.
  • the distributor 23 changes the refrigerant flow such that the refrigerant from the compressor 1 is sent to the condenser 2 through the bypass passage 22 or the refrigerant from the compressor 1 is sent to the condenser 2, not through the bypass passage 22, but through the original refrigerant passage 5.
  • a thermal sensor 24 is attached to a refrigerant outlet portion of the condenser 2 or nearby the outlet portion so as to detect the temperature of the refrigerant from the condenser 2.
  • the thermal sensor 24 may be attached at the evaporator 3 side.
  • the numeral 25 denotes a controller.
  • the controller 25 is designed to output control signals to the distributor 23 for sending the refrigerant from the compressor 1 to the condenser 2 through the bypass refrigerant passage 22 based on the detected signals which are output from the thermal sensor 24 when the sensor 24 detects an overloaded temperature, i.e., a temperature higher than usual of the refrigerant from the condenser 2.
  • the controller 25 may be composed of, for example, a micro computer.
  • the operating states thereof varies from an idling state to a low speed running state, or from the low speed running state to a high speed running state, or the like.
  • the amount of the air flow which is heat exchanged with the refrigerant passing through the condenser 2 is changed depending on the operating state of the automobile. For example, when the automobile is in the idling state, the amount of the air flow passing through the condenser 2 is small. On the contrary, when the automobile is running at a high speed, the amount of the air flow passing through the condenser 2 is large.
  • the condenser 2 actively exchanges heat, however, when the automobile is in the idling state, the performance of heat exchange with air in the condenser 2 deteriorates and thus the condenser 2 is overloaded. Under these circumstances, refrigerant cooling functions of the condenser 2 deteriorates and the supercooling degree of the liquid refrigerant flowing toward the expansion valve 4 becomes low. When the load of the condenser 2 becomes heavy, the heat exchanging performance of the evaporator 3 deteriorates. Thus, the ratio of the superheating degree of the gaseous refrigerant flowing to the compressor 1 becomes larger and the performance as a whole system deteriorates. As a result, the temperature in the car varies depending on the operating states of the car. Therefore, it is hard to realize a comfortable air conditioning environment.
  • the thermal sensor 24 when the condenser 2 is heavily loaded during an idling state, or the like, the situation is detected by the thermal sensor 24.
  • the distributor 23 functions so as to send the refrigerant from the compressor 1 to the condenser 2 through the bypass passage 22 based on the control signals from the controller 25.
  • the refrigerant flowing from the compressor 1 toward the condenser 2 exchanges heat with the refrigerant flowing from the evaporator 3 toward the compressor 1 by the accumulator 12.
  • the low temperature gaseous refrigerant returning to the compressor 1 is heated by the high temperature gaseous refrigerant flowing toward the condenser 2 and is further superheated.
  • the high temperature gaseous refrigerant flowing toward the condenser 2 is cooled by the low temperature gaseous refrigerant returning to the compressor 1, thus the liquid refrigerant sent to the expansion valve 4 is also further supercooled. Therefore, even if the load to the condenser 2 becomes large during an idling state or the like, a deterioration of the performance of the refrigerant cycle is restrained or prevented occurring. Thus, the temperature in the car become stable in spite of changes in the car operation state. Thus, a comfortable air conditioned environment is realized.
  • FIG. 12 illustrates a ninth embodiment of the refrigerant cycle system according to the present invention.
  • a bypass passage 26 (26a and 26b) is equipped within the refrigerant passage 7 connecting the condenser 2 to the expansion valve 4.
  • a heat exchanging portion 11 is provided so as to exchange heat between the refrigerant passing through the bypass passage 26 and the refrigerant passing through the refrigerant passage 6 connecting the evaporator 3 to the compressor 1.
  • an accumulator 12 having the same structure of the accumulator in the first embodiment is used.
  • the second refrigerant inlet port 17 is connected to the pipe constituting the bypass passage 26a from the condenser 2 and the second refrigerant outlet port 19 is connected to the pipe constituting the bypass passage 26b toward the expansion valve 4.
  • a distributor 23, a thermal sensor 24 and a controller 25 are provided in the same manner as per the third embodiment. In this ninth embodiment, effects which are the same as or superior to that of the eighth embodiment can be achieved.
  • FIG. 13A illustrates a tenth embodiment of the refrigerant cycle system according to the present invention.
  • This refrigerant cycle system shown in FIG. 13A is similar to the sixth embodiment, but is different in that the bypass passage 30 is opened or closed by the valve device 34 shown in FIG. 13B.
  • a thermal sensor 24 is attached to a refrigerant outlet portion of the evaporator 3 so as to detect the temperature of the refrigerant passing through the evaporator 3. Alternatively, the thermal sensor 24 may be attached to the condenser 2 side.
  • the numeral 25 denotes a controller.
  • the controller 25 is designed to output control signals to the valve device 34 for opening the bypass refrigerant passage 30, which is usually closed, based on detected signals which are output from the thermal sensor 24 when the sensor 24 detects an overloaded temperature, i.e., a temperature lower than usual, of the refrigerant of the evaporator 3.
  • an overloaded temperature i.e., a temperature lower than usual
  • the refrigerant cycle system can include a heat exchanging portion for exchanging heat between at least a part of the refrigerant passing through a refrigerant passage from the compressor to a depressurizing means by way of the condenser and at least a part of refrigerant passing through a refrigerant passage from the depressurizing means to the compressor by way of the evaporator. Therefore, the superheating degree and supercooling degree can be efficiently enhanced and, thus, the performance of the refrigerant cycle can be improved. Further, the evaporator and the condenser can be compact and superior in heat exchange performance, and the pressure loss of the refrigerant passing through the evaporator can be decreased.

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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)
  • Air-Conditioning For Vehicles (AREA)
EP96119908A 1995-12-15 1996-12-12 Système à circuit frigorifique Withdrawn EP0779481A3 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP32737595A JP3538492B2 (ja) 1995-12-15 1995-12-15 冷凍サイクル装置
JP327375/95 1995-12-15
JP32737595 1995-12-15

Publications (2)

Publication Number Publication Date
EP0779481A2 true EP0779481A2 (fr) 1997-06-18
EP0779481A3 EP0779481A3 (fr) 1999-06-09

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Application Number Title Priority Date Filing Date
EP96119908A Withdrawn EP0779481A3 (fr) 1995-12-15 1996-12-12 Système à circuit frigorifique

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EP (1) EP0779481A3 (fr)
JP (1) JP3538492B2 (fr)

Cited By (20)

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EP0915306A3 (fr) * 1997-11-06 2000-04-12 Denso Corporation Appareil frigorifigue supercritique
EP1043550A1 (fr) * 1997-12-26 2000-10-11 Zexel Corporation Cycle de refrigeration
EP1083395A1 (fr) * 1999-09-07 2001-03-14 Modine Manufacturing Company Echangeur de chaleur combiné, avec évaporateur, accumulateur et conduite d'aspiration
EP1260776A1 (fr) * 2001-05-22 2002-11-27 Zexel Valeo Climate Control Corporation Echangeur de chaleur pour système de climatisation
WO2002101304A1 (fr) * 2001-06-11 2002-12-19 Daikin Industries, Ltd. Circuit refrigerant
FR2840975A1 (fr) * 2002-06-14 2003-12-19 Valeo Climatisation Dispositif de vaporisation pour boucle de climatisation
WO2005010445A1 (fr) * 2003-06-24 2005-02-03 Modine Manufacturing Company Systeme de refrigeration
US6938432B2 (en) 2002-01-10 2005-09-06 Espec Corp. Cooling apparatus and a thermostat with the apparatus installed therein
EP1655554A2 (fr) * 2004-11-03 2006-05-10 LG Electronics, Inc. Appareil de conditionnement d'air à fonctions multiples
ITMS20080004A1 (it) * 2008-08-29 2010-02-28 Valter Angelotti Condensatore ad aria a doppio stadio per impianti frigoriferi consfruttamento del gas espanso
ITMS20080005A1 (it) * 2008-08-29 2010-02-28 Valter Angelotti Impianto frigorifero dotato di sbrinamento a gas caldocon condensatore a doppio stadio
US7694528B2 (en) 2002-06-11 2010-04-13 Denso Corporation Heat exchanging apparatus
CN101799233A (zh) * 2010-03-30 2010-08-11 南京都乐制冷设备有限公司 控制低温制冷系统中压缩机吸气温度的方法
DE10060114B4 (de) * 1999-12-09 2012-08-16 Valeo Systèmes Thermiques Klimakreis, insbesondere für ein Kraftfahrzeug
DE102013113229A1 (de) * 2013-11-29 2015-06-03 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Kälteanlage für ein Kraftfahrzeug mit Mittel- oder Heckmotor sowie Verfahren zur Klimatisierung eines Kraftfahrzeugs mit Mittel- oder Heckmotor
EP2952832A1 (fr) * 2014-06-06 2015-12-09 Vaillant GmbH Système de pompe à chaleur avec économiseur intégré
CN108413560A (zh) * 2018-02-05 2018-08-17 青岛海尔空调器有限总公司 一种空调室内机自清洁系统及其控制方法
US10962307B2 (en) 2013-02-27 2021-03-30 Denso Corporation Stacked heat exchanger
CN113639479A (zh) * 2021-07-12 2021-11-12 青岛海尔空调电子有限公司 空调系统
WO2022217851A1 (fr) * 2021-04-15 2022-10-20 芜湖美智空调设备有限公司 Système de circulation de réfrigérant et climatiseur

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KR20030085347A (ko) * 2002-04-30 2003-11-05 위니아만도 주식회사 에어컨용 어큐뮬레이터
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US6105386A (en) * 1997-11-06 2000-08-22 Denso Corporation Supercritical refrigerating apparatus
EP0915306A3 (fr) * 1997-11-06 2000-04-12 Denso Corporation Appareil frigorifigue supercritique
EP1043550A1 (fr) * 1997-12-26 2000-10-11 Zexel Corporation Cycle de refrigeration
EP1043550A4 (fr) * 1997-12-26 2003-02-19 Zexel Valeo Climate Contr Corp Cycle de refrigeration
EP1083395A1 (fr) * 1999-09-07 2001-03-14 Modine Manufacturing Company Echangeur de chaleur combiné, avec évaporateur, accumulateur et conduite d'aspiration
AU768858B2 (en) * 1999-09-07 2004-01-08 Modine Manufacturing Company Combined evaporation/accumulator/suction line heat exchanger
DE10060114B4 (de) * 1999-12-09 2012-08-16 Valeo Systèmes Thermiques Klimakreis, insbesondere für ein Kraftfahrzeug
EP1260776A1 (fr) * 2001-05-22 2002-11-27 Zexel Valeo Climate Control Corporation Echangeur de chaleur pour système de climatisation
US6895768B2 (en) 2001-06-11 2005-05-24 Daikin Industries, Ltd. Refrigerant circuit
WO2002101304A1 (fr) * 2001-06-11 2002-12-19 Daikin Industries, Ltd. Circuit refrigerant
EP1396689A4 (fr) * 2001-06-11 2012-08-01 Daikin Ind Ltd Circuit refrigerant
EP1396689A1 (fr) * 2001-06-11 2004-03-10 Daikin Industries, Ltd. Circuit refrigerant
DE10300487B4 (de) * 2002-01-10 2008-02-28 Espec K.K. Kühlvorrichtung sowie Thermostat mit einer solchen Kühlvorrichtung
US6938432B2 (en) 2002-01-10 2005-09-06 Espec Corp. Cooling apparatus and a thermostat with the apparatus installed therein
US7415836B2 (en) 2002-01-10 2008-08-26 Espec Corp Cooling apparatus and a thermostat with the apparatus installed therein
US7694528B2 (en) 2002-06-11 2010-04-13 Denso Corporation Heat exchanging apparatus
FR2840975A1 (fr) * 2002-06-14 2003-12-19 Valeo Climatisation Dispositif de vaporisation pour boucle de climatisation
WO2003106901A1 (fr) * 2002-06-14 2003-12-24 Valeo Climatisation Dispositif de vaporisation pour boucle de climatisation
WO2005010445A1 (fr) * 2003-06-24 2005-02-03 Modine Manufacturing Company Systeme de refrigeration
US6901763B2 (en) 2003-06-24 2005-06-07 Modine Manufacturing Company Refrigeration system
EP1655554A2 (fr) * 2004-11-03 2006-05-10 LG Electronics, Inc. Appareil de conditionnement d'air à fonctions multiples
EP1655554A3 (fr) * 2004-11-03 2011-08-24 LG Electronics, Inc. Appareil de conditionnement d'air à fonctions multiples
ITMS20080004A1 (it) * 2008-08-29 2010-02-28 Valter Angelotti Condensatore ad aria a doppio stadio per impianti frigoriferi consfruttamento del gas espanso
ITMS20080005A1 (it) * 2008-08-29 2010-02-28 Valter Angelotti Impianto frigorifero dotato di sbrinamento a gas caldocon condensatore a doppio stadio
CN101799233A (zh) * 2010-03-30 2010-08-11 南京都乐制冷设备有限公司 控制低温制冷系统中压缩机吸气温度的方法
CN101799233B (zh) * 2010-03-30 2012-09-05 南京都乐制冷设备有限公司 控制低温制冷系统中压缩机吸气温度的方法
US10962307B2 (en) 2013-02-27 2021-03-30 Denso Corporation Stacked heat exchanger
DE102013113229A1 (de) * 2013-11-29 2015-06-03 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Kälteanlage für ein Kraftfahrzeug mit Mittel- oder Heckmotor sowie Verfahren zur Klimatisierung eines Kraftfahrzeugs mit Mittel- oder Heckmotor
EP2952832A1 (fr) * 2014-06-06 2015-12-09 Vaillant GmbH Système de pompe à chaleur avec économiseur intégré
CN108413560A (zh) * 2018-02-05 2018-08-17 青岛海尔空调器有限总公司 一种空调室内机自清洁系统及其控制方法
WO2022217851A1 (fr) * 2021-04-15 2022-10-20 芜湖美智空调设备有限公司 Système de circulation de réfrigérant et climatiseur
CN113639479A (zh) * 2021-07-12 2021-11-12 青岛海尔空调电子有限公司 空调系统

Also Published As

Publication number Publication date
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EP0779481A3 (fr) 1999-06-09
JPH09166363A (ja) 1997-06-24

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