WO2012108112A1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

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Publication number
WO2012108112A1
WO2012108112A1 PCT/JP2011/080271 JP2011080271W WO2012108112A1 WO 2012108112 A1 WO2012108112 A1 WO 2012108112A1 JP 2011080271 W JP2011080271 W JP 2011080271W WO 2012108112 A1 WO2012108112 A1 WO 2012108112A1
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WO
WIPO (PCT)
Prior art keywords
pipe
temperature
refrigeration cycle
tube
low
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PCT/JP2011/080271
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English (en)
Japanese (ja)
Inventor
智貴 佐々木
佐藤　博
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サンデン株式会社
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Filing date
Publication date
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Publication of WO2012108112A1 publication Critical patent/WO2012108112A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide

Definitions

  • the present invention relates to a refrigeration cycle apparatus having an internal heat exchanger used in a vapor compression refrigeration cycle of a vehicle air conditioner.
  • a heat pump cycle that performs an air conditioning operation using a refrigerant such as carbon dioxide that has an internal heat exchanger as described in Patent Document 1.
  • a cycle device heat exchange is performed between a high-temperature and high-pressure liquid-phase refrigerant and a low-temperature and low-pressure gas-phase refrigerant, thereby reducing the specific enthalpy of the evaporator inlet refrigerant and increasing the refrigeration effect. Improvements in cycle efficiency and capacity have been made.
  • An object of the present invention is to provide a refrigeration cycle apparatus capable of increasing the operating efficiency and operating capacity as much as possible by increasing the amount of heat exchange in the internal heat exchanger while suppressing the suction superheat degree of the compressor small.
  • a refrigeration cycle apparatus includes: In the refrigeration cycle, one of the low-temperature and low-pressure refrigerant flowing from the evaporator outlet to the compressor inlet and the high-temperature and high-pressure refrigerant flowing from the condenser outlet to the evaporator inlet is circulated in the inner space of the inner pipe, and the other is While arranging a double pipe type internal heat exchanger circulated in the space between the inner pipe and the outer pipe, A portion of the inner tube overlaps the tube walls in the axial direction, and an inner space in the inner tube and an outer space between the inner tube and the outer tube are arranged between the overlapped tube walls.
  • the two-phase refrigerant is added to the low-temperature and low-pressure gas-phase refrigerant after passing through the evaporator, and the high-temperature and high-pressure refrigerant is more effectively cooled by the latent heat of vaporization of the two-phase refrigerant, thereby increasing the amount of heat exchange in the evaporator. can do.
  • the temperature rise of the gas-phase refrigerant is also suppressed by the high cooling function by the two-phase refrigerant, the degree of superheat at the evaporator outlet and the compressor inlet can be reduced, the performance deterioration of the compressor can be suppressed, and the suction refrigerant density To increase driving efficiency.
  • the refrigerant flow rate passing through the evaporator can be reduced, pressure loss of the refrigerant in the evaporator can be suppressed, and the refrigerating capacity and cycle efficiency can be improved. It becomes.
  • the pressure loss due to the outflow can be suppressed by the configuration in which a part of the high-temperature and high-pressure side refrigerant flows out in parallel with the flow direction of the low-temperature and low-pressure side refrigerant. Further, by appropriately adjusting the bypass flow rate and the outflow speed of the high-temperature and high-pressure side refrigerant, it is possible to provide an ejector effect. In this case, one of the power sources for sucking and conveying the low-temperature and low-pressure side refrigerant to the compressor. And contributes to the power saving of the refrigeration cycle.
  • FIG. 1 is a schematic view of a refrigeration cycle apparatus according to an embodiment of the present invention. It is a perspective view which shows the internal heat exchanger used in the refrigeration cycle apparatus of FIG. Sectional drawing which shows 1st Embodiment of the internal structure of the bypass channel periphery part in the said internal heat exchanger [(A) is AA arrow sectional drawing of (B), (B) is a longitudinal cross-sectional view, (C ) Is a front view of a double tube].
  • FIG. 8A is a cross-sectional view taken along the line AA of FIG. 8B
  • FIG. 5B is a vertical cross-sectional view showing a second embodiment of the internal structure.
  • FIG. 9B is a cross-sectional view taken along the line AA of (B), and FIG. (B) is a vertical cross-sectional view showing a third embodiment of the internal structure.
  • the figure which similarly shows 4th Embodiment of an internal structure [(A) is AA arrow sectional drawing of (B), (B) is a longitudinal cross-sectional view, (C) is a front view of a double pipe.] is there.
  • FIG. 9A is a cross-sectional view taken along the line AA of FIG. 5B
  • FIG. 5B is a vertical cross-sectional view showing a fifth embodiment of the internal structure.
  • FIG. 9B is a cross-sectional view taken along the line AA of (B), and (B) is a vertical cross-sectional view, similarly showing a sixth embodiment of the internal structure. It is a longitudinal cross-sectional view which similarly shows 7th Embodiment (A) and 8th Embodiment (B) of an internal structure. It is a diagram which shows the refrigerating cycle characteristic of the refrigerating cycle apparatus which concerns on this invention.
  • FIG. 1 is a schematic view of a refrigeration cycle apparatus 1 according to an embodiment of the present invention.
  • the refrigerant circulates in the system, and the high-temperature and high-pressure liquid-phase refrigerant that has flowed out of the condenser 2 is outside of the annular shape between the outer pipe 31 and the inner pipe 32 of the double-tube internal heat exchanger 3.
  • the refrigerant flows through the space and mainly flows into the evaporator 4 through the expansion valve 10, but a part of the refrigerant is decompressed and expanded via the bypass passage B formed in the inner pipe 32 and bypasses the evaporator 4 to bypass the inner pipe 32. Flows in.
  • the refrigerant evaporated in the evaporator 4 flows out from the evaporator 4, then flows into the inner pipe 32 of the internal heat exchanger 3, merges with the bypassed refrigerant, and then flows into the compressor 5.
  • the refrigerant compressed in the compressor 5 flows into the condenser 2 and is condensed.
  • FIG. 2 is a perspective view showing a double-pipe internal heat exchanger 3 used in the refrigeration cycle apparatus 1 of FIG.
  • a liquid phase refrigerant inflow pipe 6 that causes the liquid phase refrigerant from the condenser 2 to flow into the outer pipe 31 in the double pipe 30, and a liquid phase refrigerant that causes the liquid layer refrigerant after heat exchange in the outer pipe 31 to flow out to the expansion valve 10.
  • a tube 9 is connected.
  • FIG. 3 is a cross-sectional view showing a first embodiment of the internal structure around the bypass passage in the internal heat exchanger 3.
  • the outer pipe 31 and the inner pipe 32 are integrally formed via ribs arranged in the radial direction, and the end of the double pipe 30 on the outer peripheral wall of the open end portion on the gas phase refrigerant inflow side on the liquid phase refrigerant outflow side.
  • a cap 33 is inserted and fixed.
  • the end cap 33 has an end portion of the gas-phase refrigerant inflow pipe 8 fixed through the end wall, and an end portion of the liquid-phase refrigerant outflow pipe 7 fixed through the peripheral wall.
  • the gas-phase refrigerant inflow pipe 8 constitutes a part of the inner pipe inside the internal heat exchanger 3.
  • the inner peripheral surface of the end of the inner pipe 32 is cut into a conical surface constricted inward, and the conical surface is further divided by 3 at equal intervals in the circumferential direction (every 120 degrees).
  • Engagement surfaces 32a are formed leaving portions, and a communication groove 32b is formed by cutting a predetermined amount in the axial direction between the engagement surfaces 32a.
  • the gas-phase refrigerant inflow pipe 8 has a small-diameter portion 8A having an outer diameter that is a predetermined amount smaller than the inner diameter of the inner pipe 32 at the end connected to the end of the inner pipe 32 in the internal heat exchanger 3.
  • a portion connecting the small diameter portion 8A and the large diameter portion 8B having the same inner and outer diameter as the inner tube 32 is formed in a conical portion 8C having the same cone angle as the engagement surface 32a.
  • the outer peripheral surface of the conical portion 8C of the gas-phase refrigerant inflow pipe 8 is abutted and joined to the engagement surface 32a of the inner pipe 32, whereby the axes of the gas-phase refrigerant inflow pipe 8 and the inner pipe 32 coincide with each other.
  • An annular gap 11 is formed between the inner peripheral surface of the end portion of the pipe 32 and the outer peripheral surface of the end portion of the small diameter portion 8A of the gas-phase refrigerant inflow tube 8.
  • the communication groove 32b and the annular gap 11 communicate the annular outer space S1 between the outer tube 31 through which the high-temperature and high-pressure refrigerant flows and the inner space S2 in the inner tube 32.
  • a bypass passage B1 is formed.
  • the high-temperature and high-pressure liquid-phase refrigerant flowing in the outer space S1 exchanges heat with the low-temperature and low-pressure gas-phase refrigerant flowing in the inner space S2 via the inner wall surface of the inner tube 32.
  • a part of the liquid refrigerant is bypassed to the inner space S ⁇ b> 2 in the inner pipe 32 via the bypass passage B ⁇ b> 1 including the communication groove 32 b and the annular gap 11.
  • the bypass passage B1 is formed so that a flow resistance within a predetermined range is generated in the refrigerant flow passing therethrough, whereby a part of the high-temperature and high-pressure refrigerant is decompressed and expanded into a low-temperature and low-pressure two-phase refrigerant. It is bypassed while being converted, and functions to join the low-temperature and low-pressure gas-phase refrigerant after passing through the evaporator 4. Cycle efficiency can be improved by bypassing and joining the refrigerant in such a configuration and using the latent heat of vaporization of the bypassed refrigerant for cooling the high-temperature and high-pressure refrigerant (see FIG. 10). Further, by increasing the cooling amount of the high-temperature and high-pressure refrigerant, it is possible to keep the dryness of the refrigerant at the inlet of the evaporator 4 low, thereby further improving the refrigeration efficiency and the cycle efficiency.
  • the cooling amount due to heat exchange with the outside air in the evaporator 4 decreases by the bypass amount.
  • the refrigerating capacity and the cycle efficiency can be improved by the amount that the pressure loss due to the bypass refrigerant passing through the evaporator can be reduced.
  • the amount of cooling of the high-temperature and high-pressure refrigerant is increased using the latent heat of vaporization of the bypass refrigerant, the temperature rise due to heat exchange between the gas-phase refrigerant circulating in the inner space S2 and the high-temperature and high-pressure refrigerant can be suppressed.
  • the increase in the degree of suction superheat at the inlet of the compressor 5 can be suppressed to suppress a decrease in the durability of the compressor 5, the discharge hose, etc., and the decrease in the suction refrigerant density can be suppressed to increase the operating efficiency. it can.
  • the shape of the bypass passage B1 (passage cross-sectional area, passage length, etc.) is set so as to reduce the suction superheat degree at the compressor inlet to near zero (see FIG. 10).
  • the bypassed high-temperature / high-pressure refrigerant flow rate is set to 5 to 35% of the high-temperature / high-pressure refrigerant flow rate upstream of the bypass passage.
  • bypass passage B1 since the bypass refrigerant flows out in the same direction as the flow direction of the gas-phase refrigerant in the inner space S2, turbulence when the bypass refrigerant flows out can be suppressed, and pressure loss And the refrigerating capacity and cycle efficiency can be sufficiently increased.
  • the refrigerant since the refrigerant can be made to flow out uniformly from the annular gap 11 over the entire circumference, the disturbance suppressing function is enhanced.
  • the bypass refrigerant flowing out in the same direction can exert an ejector effect that assists the flow of the gas-phase refrigerant.
  • the driving energy of the compressor can be reduced, and the refrigerating capacity and cycle efficiency can be further increased.
  • the bypass passage B1 is preferably formed only on the upstream side of the inner pipe 32.
  • the outer pipe 31 is formed in a range (3D) that is three times as long as the outer diameter (D) of the outer pipe 31 from the end surface of the liquid refrigerant outlet side toward the downstream side of the inner pipe 32. It is preferred that By forming the bypass passage B1 at such a position, an effective heat exchange area on the tube wall surface of the inner tube 32 can be sufficiently secured, and heat exchange of the refrigerant can be performed efficiently.
  • bypass passage B1 is formed between the inner pipe (the inner pipe 32 and the gas-phase refrigerant inflow pipe 8) divided inside the internal heat exchanger 3, processing is easy and cost as described below. Reduction can be achieved.
  • the inner pipe of the double pipe protrudes from the end face of the outer pipe, and further passes through the end wall of the end cap, so that the external gas-phase refrigerant inflow pipe It becomes a structure to connect with.
  • the bypass hole which penetrates a pipe wall in an inner pipe like patent 2985882 it becomes a structure which forms a bypass hole in the inner pipe which protruded from the end surface of the outer pipe.
  • the inner tube and the outer tube of the double tube may be cut at the same end face, and welding is performed by connecting the liquid phase refrigerant inflow pipe, the outer pipe, and the gas phase refrigerant outflow pipe to the end cap. If it is applied to the joint, the number of welds can be reduced.
  • FIG. 4 is a cross-sectional view showing a second embodiment of the internal structure around the bypass passage.
  • a plurality of axially extending grooves 32c are arranged in the inner peripheral wall of the inner pipe 31 of the double pipe 30 in the circumferential direction, and the outer peripheral surface of the small-diameter portion 8A of the gas-phase refrigerant inflow pipe 8 is It is joined to the inner peripheral surface of the inner tube 32 formed to have the same diameter as the outer peripheral surface.
  • a size set so that an appropriate amount of bypass refrigerant can flow between the outer peripheral surface of the conical portion 8C between the small diameter portion 8A and the large diameter portion 8B of the gas-phase refrigerant inflow pipe 8 and the open end of the groove 32c.
  • the gap 12 is opened.
  • a bypass passage B2 that connects the outer space S1 and the inner space S2 is formed by the gap 12 and the groove 32c between the outer peripheral surface of the small diameter portion 8A and the inner peripheral surface of the inner tube 32.
  • the axial centers of the gas-phase refrigerant inflow pipe 8 and the inner pipe 32 are made to coincide with each other with high accuracy only by fitting the small-diameter portion 8A of the gas-phase refrigerant inflow pipe 8 into the inner pipe 32 and joining them.
  • the bypass passage B2 having a uniform passage area in the circumferential direction can be easily formed.
  • the groove 32c on the inner peripheral surface of the inner tube 32 can be easily formed by broaching or the like.
  • the formation of the groove 32c can increase the heat exchange area and increase the heat exchange capacity of the internal heat exchanger 3.
  • the bypass passage B2 can be easily formed using this groove.
  • FIG. 5 is a cross-sectional view showing a third embodiment of the internal structure around the bypass passage.
  • a plurality of axially extending grooves 8a are provided in the circumferential direction on the outer peripheral surface of the small diameter portion 8A of the gas-phase refrigerant inflow pipe 8, and the outer peripheral surface of the small diameter portion 8A is the inner peripheral surface of the inner tube 32. It is made to join. Further, a gap 13 having a size set so that an appropriate amount of the bypass refrigerant can flow is opened between the outer peripheral surface of the conical portion 8C and the end surface of the inner tube 32.
  • a bypass passage B3 that connects the outer space S1 and the inner space S2 is formed by the gap 13 and the groove 8a.
  • the small-diameter portion 8A of the gas-phase refrigerant inflow pipe 8 is simply fitted into the inner pipe 32 and joined, and the gas-phase refrigerant inflow pipe 8 and the inner pipe 32 are connected.
  • the shaft centers can be made to coincide with each other with high accuracy, and the bypass passage B3 having a uniform passage area in the circumferential direction can be easily formed.
  • the groove 8a of the small diameter portion 8A can be easily formed by drawing or the like.
  • tube is also employable for this invention. 6 to 8, the low-temperature and low-pressure gas-phase refrigerant is circulated in the outer space S1 between the outer tube 31 and the inner tube 32, and the high-temperature and high-pressure liquid-phase refrigerant is circulated in the inner space S2 in the inner tube 32. It is.
  • an end cap 34 fixed to the outer peripheral wall of the open end portion on the gas phase refrigerant inflow side on the liquid phase refrigerant outflow side of the double pipe 30 passes through the end wall of the liquid phase refrigerant outflow pipe 7.
  • the end is fixed, and the end of the gas-phase refrigerant inflow pipe 8 is fixed through the peripheral wall.
  • the liquid phase refrigerant outflow pipe 7 constitutes a part of the inner pipe 32 inside the internal heat exchanger 3.
  • a bypass passage B4 that bypasses the liquid-phase refrigerant flowing in the inner space S2 to the outer space S1 is formed as follows.
  • the fourth embodiment corresponds to the embodiment of FIG. 3, and the outer peripheral surface of the end portion of the inner tube 32 is cut into a conical surface that expands outward, and the conical surface is equally spaced in the circumferential direction.
  • Engagement surfaces 32d are formed at three positions (every 120 degrees), and a predetermined amount of the engagement surfaces 32d are cut in the axial direction to form communication grooves 32e.
  • the liquid-phase refrigerant outflow pipe 7 has a large-diameter portion whose inner diameter is larger by a predetermined amount than the outer diameter of the inner pipe 32 at the end connected to the end of the inner pipe 32 of the double pipe in the internal heat exchanger 3.
  • a portion connecting the large diameter portion 7A and the small diameter portion 7B having the same inner and outer diameters as the inner tube 32 is formed in a conical portion 7C having the same cone angle as the engagement surface 32d.
  • the inner peripheral surface of the conical portion 7C of the liquid-phase refrigerant outflow pipe 7 is abutted against and joined to the engagement surface 32d of the inner pipe 32, so that the axes of the inner pipe 32 and the liquid-phase refrigerant outflow pipe 7 coincide.
  • An annular gap 14 is formed between the outer peripheral surface of the end portion of the inner pipe 32 and the inner peripheral surface of the end portion of the large-diameter portion 7A of the liquid-phase refrigerant outflow tube 7.
  • FIG. 7 shows a fifth embodiment corresponding to the embodiment of FIG. 4.
  • a plurality of grooves 32 f extending in the axial direction are arranged in the circumferential direction on the outer peripheral surface of the inner pipe 32, and the end of the liquid-phase refrigerant outflow pipe 7.
  • the inner peripheral surface of the portion and the outer peripheral surface of the inner tube 32 formed to have the same diameter as the inner peripheral surface are joined. Further, a size set so that an appropriate amount of bypass refrigerant can flow between the outer peripheral surface of the conical portion 7C between the large diameter portion 7A and the small diameter portion 7B and the open end of the groove 32f.
  • the gap 15 is opened.
  • a bypass passage B5 that connects the inner space S2 and the outer space S1 is formed by the gap 15 and the groove 32f between the inner peripheral surface of the large-diameter portion 7A and the outer peripheral surface of the inner tube 32.
  • the shaft of the inner pipe 32 and the liquid-phase refrigerant outflow pipe 7 can be obtained simply by fitting the large-diameter portion 7A of the liquid-phase refrigerant outflow pipe 7 into the inner pipe 32 and joining them.
  • the centers can be made to coincide with each other with high accuracy, and the bypass passage B5 having a uniform passage area in the circumferential direction can be easily formed.
  • the groove 32f may be formed from the end surface of the large-diameter portion 7A to the depth of the pipe by a predetermined amount so that the bypass refrigerant can flow out in parallel with the flow direction of the gas-phase refrigerant.
  • FIG. 8 shows a sixth embodiment corresponding to the embodiment of FIG. 5, and a plurality of grooves 7 a extending in the axial direction are arranged in the circumferential direction on the inner peripheral surface of the large-diameter portion 7 ⁇ / b> A of the liquid-phase refrigerant outflow pipe 7. Then, the inner peripheral surface of the large diameter portion 7A and the outer peripheral surface of the inner tube 32 are joined. Further, as in the fifth embodiment, a gap 15 having a size set so that an appropriate amount of bypass refrigerant can flow between the inner peripheral surface of the conical 9C and the end surface of the inner tube 32 is opened.
  • the bypass 15 that communicates the inner space S2 and the outer space S1 is formed by the gap 15 and the groove 7a.
  • the present embodiment also includes the inner pipe 32 and the liquid-phase refrigerant outflow pipe 7 simply by fitting the large-diameter portion 7 ⁇ / b> A of the liquid-phase refrigerant outflow pipe 7 into the inner pipe 32.
  • the bypass passage 6 having a uniform passage area in the circumferential direction can be easily formed.
  • the bypass passage B is formed by connecting the liquid-phase refrigerant outflow pipe 7 or the gas-phase refrigerant inflow pipe 8 in the internal heat exchanger 3 to the inner pipe 32 as a divided inner pipe.
  • the bypass passage B may be formed without dividing the inner pipe 32.
  • a bypass passage B7 is formed by an annular gap inside the pipe member 51 that is fitted and fixed, or a plurality of axially formed grooves 51a formed in this portion.
  • the outer space S1 is fitted into a plurality of communication holes 32h intermittently formed around the inner pipe 32 through which the high-temperature and high-pressure liquid refrigerant flows, and the inner circumference of the inner pipe 32.
  • a bypass passage B8 is formed by an annular gap outside the pipe member 61 fixed in place or a plurality of axially formed grooves 61a formed in this portion.
  • the refrigeration cycle apparatus according to the present invention is widely used in a vapor compression refrigeration cycle of a vehicle air conditioner.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un dispositif à cycle de réfrigération permettant d'augmenter la quantité de chaleur échangée par un échangeur de chaleur interne par rapport à l'état de la technique tout en maintenant une capacité de fonctionnement et un rendement d'exploitation de haut niveau. Ce dispositif à cycle de réfrigération a un échangeur de chaleur interne du type à double tube, comportant un tube intérieur (32) dans lequel un milieu de refroidissement qui circule dans le cycle de réfrigération s'écoule depuis la sortie d'un évaporateur jusqu'à l'entrée d'un compresseur, et un tube extérieur (31) dans lequel le milieu de refroidissement s'écoule depuis la sortie d'un condenseur jusqu'à l'entrée de l'évaporateur. Un passage de contournement (B1), qui entraîne une partie du milieu de refroidissement en phase liquide haute température, haute pression s'écoulant dans l'espace extérieur (S1) entre le tube extérieur (31) et le tube intérieur (32) à passer dans l'espace intérieur (S2) à l'intérieur du tube intérieur (32), est formé entre les parois de tube d'un tuyau d'amenée du milieu de refroidissement en phase gazeuse (8) et le tube intérieur (32), qui se recouvrent dans la direction axiale quand la partie à petit diamètre (8A) au niveau de l'extrémité du tuyau d'amenée du milieu de refroidissement en phase gazeuse (8) est insérée dans une extrémité du tube intérieur (32).
PCT/JP2011/080271 2011-02-08 2011-12-27 Dispositif à cycle de réfrigération WO2012108112A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011025091A JP2012163281A (ja) 2011-02-08 2011-02-08 冷凍サイクル装置
JP2011-025091 2011-02-08

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WO2012108112A1 true WO2012108112A1 (fr) 2012-08-16

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115468323A (zh) * 2022-08-26 2022-12-13 肯德环境科技工程(上海)有限公司 一种多级冷却循环系统

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20190001142A (ko) * 2017-06-26 2019-01-04 엘지전자 주식회사 열교환장치
KR102125025B1 (ko) * 2018-05-08 2020-06-19 김봉석 냉동장치의 액열기

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005083741A (ja) * 2003-09-05 2005-03-31 Lg Electronics Inc 熱交換器及び冷媒切り替え手段を有する空調装置
JP2007101043A (ja) * 2005-10-04 2007-04-19 Calsonic Kansei Corp ヒートサイクル
JP2007240041A (ja) * 2006-03-07 2007-09-20 Tgk Co Ltd 膨張弁
JP2008149812A (ja) * 2006-12-15 2008-07-03 Tgk Co Ltd 自動車用空調装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005083741A (ja) * 2003-09-05 2005-03-31 Lg Electronics Inc 熱交換器及び冷媒切り替え手段を有する空調装置
JP2007101043A (ja) * 2005-10-04 2007-04-19 Calsonic Kansei Corp ヒートサイクル
JP2007240041A (ja) * 2006-03-07 2007-09-20 Tgk Co Ltd 膨張弁
JP2008149812A (ja) * 2006-12-15 2008-07-03 Tgk Co Ltd 自動車用空調装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115468323A (zh) * 2022-08-26 2022-12-13 肯德环境科技工程(上海)有限公司 一种多级冷却循环系统

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