WO2016067551A1 - Échangeur thermique empilé - Google Patents

Échangeur thermique empilé Download PDF

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Publication number
WO2016067551A1
WO2016067551A1 PCT/JP2015/005262 JP2015005262W WO2016067551A1 WO 2016067551 A1 WO2016067551 A1 WO 2016067551A1 JP 2015005262 W JP2015005262 W JP 2015005262W WO 2016067551 A1 WO2016067551 A1 WO 2016067551A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
gas
heat
supercooling
plate
Prior art date
Application number
PCT/JP2015/005262
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English (en)
Japanese (ja)
Inventor
高橋　栄三
Original Assignee
株式会社デンソー
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
Priority claimed from JP2015154477A external-priority patent/JP6497262B2/ja
Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Priority to DE112015004908.8T priority Critical patent/DE112015004908T5/de
Publication of WO2016067551A1 publication Critical patent/WO2016067551A1/fr

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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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/02—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the heat-exchange media travelling at an angle to one another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning

Definitions

  • the present disclosure relates to a stacked heat exchanger that exchanges heat between a refrigerant and a heat medium in a refrigeration cycle.
  • Laminate that heat-exchanges refrigerant and heat medium by alternately forming refrigerant flow paths and heat medium flow paths between heat transfer plates by overlapping a plurality of substantially flat plate heat transfer plates at intervals.
  • a type heat exchanger is known.
  • Patent Document 1 discloses an integrated cylindrical modulator that separates the gas-liquid refrigerant flowing out of the heat exchanger and stores the refrigerant.
  • the present disclosure is a stacked heat exchanger including a gas-liquid separation unit that separates gas-liquid refrigerant and a supercooling unit that supercools liquid-phase refrigerant that has flowed out of the gas-liquid separation unit.
  • An object of the present invention is to provide a stacked heat exchanger that can be downsized and can reduce dead space on mounting.
  • the stacked heat exchanger includes a heat exchange unit and a gas-liquid separation unit.
  • the heat exchange unit exchanges heat between the refrigerant of the refrigeration cycle and the heat medium.
  • the gas-liquid separation unit separates the gas-liquid of the refrigerant that has flowed into the interior and stores excess refrigerant in the refrigeration cycle.
  • the heat exchange part is formed by laminating and joining a plurality of first plate members.
  • a plurality of refrigerant passages through which the refrigerant flows and a plurality of heat medium passages through which the heat medium flows are formed between the plurality of first plate-like members.
  • the plurality of refrigerant passages and the plurality of heat medium passages are arranged side by side in the stacking direction of the plurality of first plate-like members.
  • a heat is exchanged between the condensing unit that heat-exchanges the gas-phase refrigerant and the heat medium to condense the gas-phase refrigerant, and the liquid-phase refrigerant and the heat medium separated by the gas-liquid separation unit.
  • a supercooling section that supercools the phase refrigerant is provided side by side in a direction orthogonal to the stacking direction.
  • the condensing part and the supercooling part are partitioned by a heat insulating part.
  • both the condensing part and the supercooling part are arranged in one refrigerant passage, the heat damage that the low-temperature liquid phase refrigerant flowing through the supercooling part is heated by the heat of the high-temperature refrigerant flowing through the condensing part may occur. There is sex. On the other hand, according to the 1st mode of this indication, generation of heat damage can be controlled by partitioning a condensation part and a supercooling part with a heat insulation part in a refrigerant passage.
  • the stacked heat exchanger includes a heat exchange unit and a gas-liquid separation unit.
  • the heat exchange unit exchanges heat between the refrigerant of the refrigeration cycle and the heat medium.
  • the gas-liquid separation unit separates the gas-liquid of the refrigerant that has flowed into the interior and stores excess refrigerant in the refrigeration cycle.
  • the heat exchanging part has a plurality of first plate-like members stacked, and is formed by stacking and joining a plurality of first plate-like members. Between the first plate-like members, a refrigerant passage through which a refrigerant flows or a plurality of heat medium passages through which a heat medium flows is formed. Between the first plate-like members, a plurality of refrigerant passages through which the refrigerant flows and a plurality of heat medium passages through which the heat medium flows are formed. The plurality of refrigerant passages and the plurality of heat medium passages are alternately arranged in the stacking direction of the plurality of first plate-like members.
  • a heat is exchanged between the condensing unit that heat-exchanges the gas-phase refrigerant and the heat medium to condense the gas-phase refrigerant, and the liquid-phase refrigerant and the heat medium separated by the gas-liquid separation unit.
  • a supercooling section that supercools the phase refrigerant is provided side by side in a direction orthogonal to the stacking direction.
  • a heat insulating part that insulates the condensing part and the supercooling part is disposed between the condensing part and the supercooling part.
  • FIG. 18 is a cross-sectional view taken along line XIX-XIX in FIG. It is an enlarged view of the XX part of FIG. It is sectional drawing which shows the heat exchanger which concerns on 5th Embodiment. It is a front view which shows the heat exchanger in other embodiment (3).
  • the heat exchanger shown in FIG. 1 constitutes a refrigeration cycle of a vehicle air conditioner.
  • the heat exchanger is a condenser that condenses the high-pressure side refrigerant by exchanging heat between the high-pressure side refrigerant and the cooling water of the refrigeration cycle.
  • the cooling water of the present embodiment corresponds to the heat medium of the present disclosure.
  • cooling water for example, a liquid containing at least ethylene glycol, dimethylpolysiloxane or nanofluid, or an antifreeze liquid can be used.
  • ethylene glycol antifreeze (LLC) is used as the cooling water.
  • the heat exchanger forms a refrigerant flow path and a heat medium flow path alternately between the heat transfer plates by overlapping a plurality of substantially flat plate heat transfer plates with a space therebetween. Is a stacked heat exchanger for exchanging heat.
  • the heat exchanger includes a heat exchanging unit 1 for exchanging heat between the refrigerant of the refrigeration cycle and the cooling water, and a gas-liquid separation unit 2 for separating the gas-liquid of the refrigerant flowing into the interior and storing excess refrigerant in the refrigeration cycle. I have.
  • the heat exchanging portion 1 is integrally formed by laminating and joining a large number of first plate members 11.
  • the plate stacking direction of the first plate-like member 11 (the left-right direction in the examples of FIGS. 1 and 2) is referred to as the stacking direction.
  • one end side in the plate stacking direction (right side in the examples of FIGS. 1 and 2) is referred to as one end side in the stacking direction.
  • the other end side in the plate stacking direction left side in the examples of FIGS. 1 and 2) is referred to as the other end side in the stacking direction.
  • the first plate member 11 is a long and substantially rectangular metal plate (in this example, made of aluminum or aluminum alloy).
  • the heat exchanger of this embodiment is arrange
  • the substantially laminating direction is a direction substantially orthogonal to the plate surface of the first plate-like member 11.
  • the multiple first plate-like members 11 are joined to each other by brazing, with the overhanging portions 111 being laminated together.
  • the multiple first plate-like members 11 are arranged so that the protruding directions of the overhang portions 111 are the same (substantially right in the example of FIG. 1).
  • a plurality of refrigerant passages 12 through which a refrigerant flows and a plurality of cooling water passages 13 through which cooling water flows are formed between the plurality of first plate-like members 11.
  • the cooling water passage 13 of the present embodiment corresponds to the heat medium passage of the present disclosure.
  • one of the first plate members 11a protrudes partly toward the other first plate member 11b.
  • a protruding portion 112 (second protruding portion) is provided.
  • the protrusion 112 is joined to the other first plate member 11b.
  • the first plate-like member 11a the first surface on the side where the protruding portion 112 protrudes, and the other first plate-like member 11b facing the first surface of the first plate-like member 11a.
  • a refrigerant passage 12 is formed between the first surface and the first surface.
  • the second surface which is the surface opposite to the first surface and the second of the other first plate-like member 11b facing the second surface of the first plate-like member 11a.
  • a cooling water passage 13 is formed between the surfaces.
  • the plurality of refrigerant passages 12 and the plurality of cooling water passages 13 are arranged side by side in the stacking direction. More specifically, the refrigerant passages 12 and the cooling water passages 13 are disposed (arranged in parallel) so as to be alternately stacked one by one in the stacking direction.
  • the first plate-like member 11 serves as a partition wall that partitions the refrigerant passage 12 and the cooling water passage 13. Heat exchange between the refrigerant flowing through the refrigerant passage 12 and the cooling water flowing through the cooling water passage 13 is performed via the first plate member 11.
  • the refrigerant passage 12 is disposed on the outermost side in the stacking direction.
  • the refrigerant passage 12 has a condensing part 121 and a supercooling part 122.
  • the condensing unit 121 heat-exchanges the gas-phase refrigerant and the cooling water to condense the gas-phase refrigerant.
  • the supercooling unit 122 supercools the liquid phase refrigerant by exchanging heat between the liquid phase refrigerant separated by the gas-liquid separation unit 2 and the cooling water.
  • the condensing part 121 and the supercooling part 122 are provided along with the direction orthogonal to the lamination direction.
  • the condensing part 121 and the supercooling part 122 are provided along with the longitudinal direction of the 1st plate-shaped member 11, ie, the gravity direction. More specifically, in the refrigerant passage 12, the condensing unit 121 is disposed above the supercooling unit 122 in the gravity direction.
  • the protrusion 112 formed on one first plate-like member 11a is joined to the other first plate-like member 11b.
  • the refrigerant passage 12 can be partitioned into a condensing portion 121 and a supercooling portion 122.
  • the protrusion 112 has a shape in which the surface facing the cooling water passage 13 of the first plate-like member 11a is recessed, and this recessed portion communicates with the cooling water passage 13 and Part of it.
  • the condensing part 121 and the supercooling part 122 are partitioned by the heat insulating part 123.
  • the heat insulating portion 123 of this embodiment constitutes a part of the cooling water passage 13.
  • the heat exchanging unit 1 includes the first tank space 14 for condensation, the second tank space 15 for condensation, and the first tank for supercooling in addition to the refrigerant passage 12 and the cooling water passage 13 described above.
  • a space 16 a supercooling second tank space 17, a cooling water first tank space 18, and a cooling water second tank space 19 are provided.
  • the first plate member 11 includes a first tank space for condensation 14, a second tank space for condensation 15, a first tank space 16 for supercooling, A second tank space 17 for supercooling, a first tank space 18 for cooling water, and a second tank space 19 for cooling water are formed.
  • the first tank space 14 for condensation and the second tank space 15 for condensation perform refrigerant distribution and aggregation with respect to the condensing portions 121 of the plurality of refrigerant passages 12.
  • the first subcooling tank space 16 and the second subcooling tank space 17 distribute and collect refrigerant to the subcooling sections 122 of the plurality of refrigerant passages 12.
  • the cooling water first tank space 18 and the cooling water second tank space 19 distribute and collect the cooling water to the plurality of cooling water passages 13.
  • the condensation first tank space 14 distributes the refrigerant to the condensing portions 121 of the plurality of refrigerant passages 12.
  • the condensation second tank space 15 collects refrigerant with respect to the condensing portions 121 of the plurality of refrigerant passages 12.
  • the first tank space 16 for supercooling distributes the refrigerant to the supercooling portions 122 of the plurality of refrigerant passages 12.
  • the supercooling second tank space 17 collects refrigerant with respect to the supercooling portions 122 of the plurality of refrigerant passages 12.
  • the first tank space 18 for cooling water distributes the cooling water to the plurality of cooling water passages 13.
  • the second tank space 19 for cooling water collects cooling water with respect to the plurality of cooling water passages 13.
  • Condensing first tank space 14 Condensing second tank space 15, Supercooling first tank space 16, Supercooling second tank space 17, Cooling water first tank space 18, and Cooling water second tank space
  • Reference numeral 19 denotes a communication hole formed in the first plate-like member 11.
  • the direction in which the condensing unit 121 and the supercooling unit 122 are adjacent to each other in the refrigerant passage 12 is referred to as an arrangement direction.
  • a direction perpendicular to both the arrangement direction and the stacking direction is referred to as a width direction.
  • the arrangement direction coincides with the gravity direction and the longitudinal direction of the first plate-like member 11.
  • the width direction coincides with the horizontal direction.
  • the first tank space 18 for cooling water is formed in the cooling water passage 13 of the heat exchange unit 1 on the side having the supercooling part 122 in the arrangement direction (below the gravity direction) and in the width direction. It is arranged on one side (left side in the example of FIG. 4).
  • the second cooling water tank space 19 is on the side having the condensing unit 121 in the arrangement direction (upward in the gravity direction) and on the other side in the width direction (in the example of FIG. 4). (Right).
  • the cooling water flows from the supercooling part 122 in the arrangement direction toward the condensing part 121 and in the direction from one side in the width direction toward the other side. .
  • the cooling water flows from the lower side to the upper side in the direction of gravity and from the left side to the right side in FIG.
  • the first tank space 14 for condensing is a region farther from the supercooling part 122 than the center part of the condensing part 121 in the arrangement direction in the condensing part 121 of the heat exchange part 1 (upper side in the gravity direction). ) And on one side in the width direction (left side in the example of FIG. 5).
  • the second tank space 15 for condensation is a region closer to the supercooling part 122 than the center part of the condensation part 121 in the arrangement direction in the condensation part 121 of the heat exchange part 1 (lower side in the gravity direction), and the width direction. It is arranged on the other side (right side in the example of FIG. 5).
  • the first tank space 16 for supercooling is a region closer to the condensing part 121 than the central part of the supercooling part 122 in the arrangement direction in the supercooling part 122 of the heat exchange part 1 (upward in the gravity direction), and It is arranged on one side in the width direction (left side in the example of FIG. 5).
  • the second tank space for supercooling 17 is a region far from the condensing unit 121 in the arrangement direction (lower side in the gravity direction) of the supercooling unit 122 of the heat exchange unit 1 and the other side in the width direction (in FIG. 5). It is arranged on the right side in the example.
  • a refrigerant goes to the supercooling part 122 from the condensing part 121 of an arrangement direction, and is changed from one side to the other side of the width direction. It flows in the direction of heading.
  • the refrigerant flows from the upper side to the lower side in the direction of gravity and from the left side to the right side in FIG.
  • the refrigerant flow flowing through the refrigerant passage 12 and the cooling water flow flowing through the cooling water passage 13 intersect each other. That is, when the heat exchange unit 1 is viewed from the stacking direction, the refrigerant flow flowing through the condensing unit 121 and the cooling water flow flowing through the cooling water passage 13 intersect each other, and the refrigerant flow and cooling flowing through the supercooling unit 122 The cooling water flow flowing through the water passage 13 intersects.
  • the condensing side inner part which divides
  • Fins 51 are provided.
  • the condensation-side inner fins 51 are offset fins in which the wall portions 51a that divide the condensation-side narrow channel 121a are arranged in a staggered manner along the refrigerant flow direction (that is, the arrangement direction).
  • the supercooling unit 122 divides the flow path in the supercooling unit 122 into a plurality of subcooling side narrow flow channels 122 a to promote heat exchange between the refrigerant and the cooling water.
  • Side inner fins 52 are provided.
  • the supercooling side inner fin 52 is a straight fin in which a wall portion 52a dividing the supercooling side narrow channel 122a extends linearly in the refrigerant flow direction (that is, the arrangement direction).
  • cooling water side inner fins 53 are also provided in the cooling water passage 13.
  • an offset fin is employed as the cooling water side inner fin 53.
  • the condensation-side inner fin 51, the supercooling-side inner fin 52, and the cooling water-side inner fin 53 are joined to both adjacent first plate-like members 11 by brazing.
  • the first joint 31 is provided on the outermost plate-like member 11 ⁇ / b> A located on the outermost side on one end side in the stacking direction among the multiple first plate-like members 11 constituting the heat exchange unit 1.
  • the 2nd joint 32, the 1st cooling water pipe 33, and the 2nd cooling water pipe 34 are attached.
  • 1st joint 31 is a member for joining refrigerant piping, and forms the refrigerant inlet of a heat exchanger.
  • the 2nd joint 32 is a member for joining refrigerant
  • the first cooling water pipe 33 forms a cooling water inlet of the heat exchanger.
  • the second cooling water pipe 34 forms a cooling water outlet of the heat exchanger.
  • the first joint 31 is disposed at a portion corresponding to the first tank space 14 for condensation in the endmost plate member 11 ⁇ / b> A.
  • the 2nd joint 32 is arrange
  • the 1st cooling water pipe 33 is arrange
  • the 2nd cooling water pipe 34 is arrange
  • the first ceiling plate 11 ⁇ / b> B is thicker than the other first plate-like members 11 and has a longer length in the stacking direction of the overhanging portion 111.
  • a gas-liquid separation unit 2 is connected to the surface of the first ceiling plate 11B opposite to the heat exchange unit 1.
  • the gas-liquid separator 2 is integrally formed by stacking and joining a plurality of second plate-like members 21 to each other.
  • the stacking direction of the second plate member 21 is parallel to the stacking direction (plate stacking direction) of the first plate member 11.
  • the broken line in FIG. 2 has shown the liquid level of the liquid phase refrigerant
  • the second plate-like member 21 is equal in length to the first plate-like member 11 in the arrangement direction and in the width direction.
  • the second plate member 21 has a longer length in the stacking direction of the overhanging portion 211 than the first plate member 11.
  • a plurality of gas-liquid separation passages 22 through which the refrigerant flowing from the condensing unit 121 of the heat exchange unit 1 flows are formed between the plurality of second plate-like members 21.
  • the second plate-shaped member 21 is provided with a through hole (not shown) so that adjacent gas-liquid separation passages 22 communicate with each other.
  • the length of the gas-liquid separation passage 22 in the stacking direction is longer than both the length of the refrigerant passage 12 in the stacking direction and the length of the cooling water passage 13 in the stacking direction.
  • the inner fin is not arrange
  • the second plate-like member 21 located on the outermost side on the other end side in the stacking direction is referred to as a second ceiling plate 21B.
  • the second ceiling plate 21 ⁇ / b> B is thicker than the other second plate-like members 21.
  • Ribs 212 are provided on the second ceiling board 21B.
  • the rib 212 is formed by denting a part of the second ceiling plate 21B toward one end side (heat exchange part 1) in the stacking direction.
  • a reinforcing plate 212A is joined to the second ceiling plate 21B of the present embodiment so as to cover the rib 212.
  • the strength of the gas-liquid separation unit 2 can be improved by the rib 212.
  • the strength of the gas-liquid separator 2 may be improved by adding a reinforcing plate or the like inside the gas-liquid separator 2. Further, the strength of the gas-liquid separation unit 2 may be further improved by joining a part of the multiple second plate-like members 21 constituting the gas-liquid separation unit 2 by surface matching or the like.
  • a first through hole 113 is provided in a portion corresponding to the second tank space 15 for condensation in the first ceiling plate 11B.
  • the condensing second tank space 15 communicates with the gas-liquid separation passage 22 via the first through hole 113.
  • the first through-hole 113 of the present embodiment has a heat exchange section side outflow section for flowing out the refrigerant condensed in the condensing section 121 to the outside, and the refrigerant condensed in the condensing section 121 in the gas-liquid separation section 2. It fulfills the function of the inflow part on the gas-liquid separation part side. Therefore, it can be said that the heat exchanger of this embodiment has the heat exchange part side outflow part and the gas-liquid separation part side inflow part directly connected by the first through hole 113.
  • a second through hole 114 is provided in a portion corresponding to the first tank space 16 for supercooling in the first ceiling plate 11B.
  • the first tank space 16 for supercooling communicates with the gas-liquid separation passage 22 through the second through hole 114.
  • the second through-hole 114 of the present embodiment has a gas-liquid separation part side outflow part that causes the liquid-phase refrigerant separated in the gas-liquid separation part 2 to flow out to the outside, and the gas-liquid separation part 2 has gas. It fulfills the function of the heat exchange section side inflow section that causes the liquid phase separated liquid to flow into the supercooling section 122. Therefore, it can be said that the heat exchanger of this embodiment has the heat exchange part inflow part and the gas-liquid separation part side outflow part directly connected by the second through-hole 114.
  • the condensing part 121 and the supercooling part 122 are provided side by side in the arrangement direction in the refrigerant passage 12 formed between the first plate-like members 11. Thereby, both the condensing part 121 and the supercooling part 122 can be arrange
  • the condensing part 121 and the supercooling part 122 are partitioned by the heat insulating part 123. According to this, it is possible to suppress the occurrence of heat damage in which the low-temperature liquid-phase refrigerant flowing through the supercooling unit 122 is heated by the heat of the high-temperature refrigerant flowing through the condensing unit 121.
  • the heat insulating portion 123 is configured as a part of the cooling water passage 13. Since the heat capacity of the cooling water is larger than that of the refrigerant, the heat insulation part 123 through which the cooling water circulates further suppresses the thermal interference between the refrigerant that circulates in the condensing part 121 and the refrigerant that circulates in the supercooling part 122. Heat exchange with water can be promoted.
  • the cooling water flows into the protrusion 112 of the heat insulating portion 123 from the gap between the walls of the cooling water side inner fin 53 (offset fin), the cooling water flows inside the protrusion 112.
  • the cooling water has a large heat capacity with respect to the refrigerant, and the cooling water flowing through the protrusion 112 is heat-exchanged with both the refrigerant flowing through the supercooling unit 122 and the refrigerant flowing through the condensing unit 121. For this reason, heat exchange between the refrigerant and the cooling water can be promoted while suppressing thermal interference between the refrigerants.
  • the heat insulating portion 123 is configured by the protruding portion 112 formed by bending a part of the first plate-like member 11. For this reason, the heat insulation part 123 can be set without deteriorating the assembly workability of the heat exchange part 1. Furthermore, the increase in the number of parts for setting the heat insulation part 123 can also be prevented.
  • the cooling water flows from the supercooling unit 122 to the condensing unit 121 and from one side in the width direction to the other side. ing.
  • the refrigerant flows from the condensing unit 121 to the supercooling unit 122 and from one side in the width direction to the other side, as indicated by broken line arrows in FIG. ing. That is, in this embodiment, when the heat exchange unit 1 is viewed from the stacking direction, the refrigerant flow flowing through the refrigerant passage 12 and the cooling water flow flowing through the cooling water passage 13 are crossed. According to this, in each of the condensing part 121 and the supercooling part 122, the heat exchange efficiency of a refrigerant
  • the surface of the first plate-like member 11 facing the refrigerant passage 12 in this embodiment is shown in FIG.
  • the condensing side inner fin 51 or the supercooling side inner fin 52 is arranged in a region indicated by point hatching.
  • the vicinity of the portion forming the tank spaces 14 to 19 is a dead water area.
  • the dead water area is an area where the inner fins 51 and 52 cannot be physically disposed, or a space for facilitating the flow of the refrigerant into the inner fins 51 and 52.
  • the cooling water flow is caused to flow from the supercooling unit 122 and flow to the condensing unit 121.
  • the inner fins 51 and 52 can also be arrange
  • straight fins are adopted as the supercooling side inner fins 52. According to this, in the supercooling part 122, the pressure loss of a refrigerant
  • the heat exchange part 1 and the gas-liquid separation part 2 are directly connected by the 1st through-hole 113 and the 2nd through-hole 114 which were formed in the 1st ceiling board 11B. According to this, since it is not necessary to provide piping for connecting the heat exchange unit 1 and the gas-liquid separation unit 2, it is possible to reduce the mounting space for the heat exchanger and the number of components.
  • the heat exchanger is configured to make a U-turn of the refrigerant flow in the gas-liquid separator 2. Since the gas-liquid separator 2 corresponds to an enlarged portion of the refrigerant flow path, the bending loss of the refrigerant flow path can be ignored. For this reason, it is possible to make the refrigerant flow U-turn while suppressing the occurrence of bending loss or the like of the refrigerant.
  • the gas-liquid separation space in the gas-liquid separation unit 2 is constituted by a large number of second plate-like members 21.
  • the condensing side inner fin 51 is arrange
  • the second plate-like member 21 is cooled by the liquid phase refrigerant in the gas-liquid separation unit 2, even when bubbles (gas phase refrigerant) are slightly mixed when flowing into the gas-liquid separation unit 2, The bubbles are cooled and condensed by exchanging heat with the second plate member 21.
  • the gas-liquid separation property of the gas-liquid separation unit 2 can be improved.
  • FIG. 9 is a drawing corresponding to FIG. 3 of the first embodiment.
  • the heat insulation part 123 of this embodiment is an air layer in which air exists. More specifically, the third plate member 41 is joined to one first plate member 11 a of the two first plate members 11 that define the coolant passage 12. The 3rd plate-shaped member 41 is joined to the surface which faces the refrigerant path 12 of one 1st plate-shaped member 11a.
  • the third plate member 41 is provided with a protruding portion 412 that partially protrudes toward the other first plate member 11b.
  • the protrusion 412 is joined to the other first plate member 11b.
  • the protrusion 412 can partition the refrigerant passage 12 into a condensing part 121 and a supercooling part 122.
  • the heat insulating portion 123 is formed of an air layer, even if the flow of the cooling water stops, the heat interference between the refrigerant between the condensing unit 121 and the supercooling unit 122. Can be reduced.
  • the heat insulation part 123 is comprised by adding the 3rd plate-shaped member 41. FIG. For this reason, the heat insulation part 123 can be set without deteriorating the assembly workability of the heat exchange part 1.
  • the third embodiment differs from the first embodiment in the configurations of the heat exchange unit 1 and the gas-liquid separation unit 2.
  • the broken line in FIG. 11 has shown the liquid level of the liquid phase refrigerant
  • the supercooling first tank space 16 of the present embodiment collects refrigerants with respect to the supercooling portions 122 of the plurality of refrigerant passages 12.
  • the subcooling second tank space 17 distributes the refrigerant to the subcooling portions 122 of the plurality of refrigerant passages 12.
  • the second joint 32 communicates with the first tank space 16 for supercooling.
  • the overhanging portion 211 of the second plate-like member 21 overhangs (protrudes) toward the other end side in the stacking direction. That is, in the present embodiment, the protruding direction (projecting direction) of the protruding portion 211 of the second plate-shaped member 21 is opposite to the protruding direction (projecting direction) of the protruding portion 111 of the first plate-shaped member 11. It has become.
  • the second plate-like member 21 located on the outermost side on one end side in the stacking direction is referred to as a third ceiling plate 21A.
  • the third ceiling plate 21A is thicker than the other second plate-like member 21.
  • the first ceiling plate 11B of the heat exchanging unit 1 is joined to the surface of the third ceiling plate 21A opposite to the gas-liquid separation unit 2.
  • a third through hole 213 is provided in a portion of the third ceiling plate 21A corresponding to the first through hole 113 of the first ceiling plate 11B.
  • the outer peripheral edge portion of the third through hole 213 is directly joined to the outer peripheral edge portion of the first through hole 113.
  • the condensation second tank space 15 communicates with the gas-liquid separation passage 22 via the first through hole 113 and the third through hole 213.
  • the first through hole 113 of the present embodiment functions as a heat exchange section side outflow section that causes the refrigerant condensed in the condensing section 121 to flow out to the outside.
  • the third through-hole 213 of the present embodiment functions as a gas-liquid separation unit side inflow portion that causes the refrigerant condensed in the condensing unit 121 to flow into the gas-liquid separation unit 2.
  • the outer peripheral edge portion of the third through hole 213 is directly joined to the outer peripheral edge portion of the first through hole 113. Therefore, it can be said that the heat exchanger of this embodiment has the heat exchange part side outflow part and the gas-liquid separation part side inflow part directly connected without interposing other members.
  • a fourth through hole 214 is provided in a portion of the third ceiling plate 21A corresponding to the second through hole 114 of the first ceiling plate 11B.
  • the outer peripheral edge portion of the fourth through hole 214 is directly joined to the outer peripheral edge portion of the second through hole 114.
  • the supercooling second tank space 17 communicates with the gas-liquid separation passage 22 via the second through hole 114 and the fourth through hole 214.
  • the fourth through-hole 214 of the present embodiment functions as a gas-liquid separation part side outflow part that causes the liquid-phase refrigerant separated in the gas-liquid separation part 2 to flow out.
  • the second through-hole 114 of the present embodiment functions as a heat exchange section side inflow section that allows the liquid-phase refrigerant separated from the gas-liquid separation section 2 to flow into the supercooling section 122.
  • the outer peripheral edge portion of the fourth through hole 214 is directly joined to the outer peripheral edge portion of the second through hole 114. Therefore, it can be said that the heat exchanger of this embodiment has the heat exchange part side inflow part and the gas-liquid separation part side outflow part directly connected without interposing other members.
  • the third ceiling plate 21 ⁇ / b> A is provided with a recess 215.
  • the recess 215 is formed by denting a part of the third ceiling plate 21A toward the other end side in the stacking direction.
  • a gap can be formed between the first ceiling plate 11B and the third ceiling plate 21A, that is, between the heat exchange unit 1 and the gas-liquid separation unit 2. it can.
  • the multiple first plate-like members 11 constituting the heat exchanging portion 1 are substantially cylindrical protruding portions that protrude toward one end side or the other end side in the stacking direction. 115.
  • the protrusions 115 are provided at portions corresponding to the four corners of the first plate-like member 11, the second tank space 15 for condensation, and the first tank space 16 for supercooling.
  • the first tank space for condensation 14, the second tank space for condensation 15, the first tank space for supercooling 16, the second tank space for supercooling 17, the first tank space for cooling water 18, and the cooling Water second tank spaces 19 are respectively formed.
  • the protruding portion 115 formed on one first plate-like member 11a and the protruding portion 115 formed on the other first plate-like member 11b are fitted together, and the first tank space for condensation 14, the condensation A second tank space 15, a supercooling first tank space 16, a supercooling second tank space 17, a cooling water first tank space 18 and a cooling water second tank space 19 are formed.
  • first plate-like members 11 constituting the heat exchanging portion 1, between the central portion in the laminating direction and the outermost first plate-like member 11 on one end side in the laminating direction.
  • One first plate-like member 11 located in a region far from the liquid separation part 2 has a closing part 116 that closes the protruding part 115 constituting the first tank space 14 for condensation. Thereby, the 1st tank space 14 for condensation is divided into two spaces in the lamination direction.
  • One first plate-like member 11 located in a region closer to the gas-liquid separation unit 2 than the gas-liquid separation unit 2 has a closing part 116 that closes the protruding part 115 that constitutes the second tank space 15 for condensation.
  • the second tank space for condensation 15 is partitioned into two spaces in the stacking direction.
  • closing portion 116 is formed integrally with the protruding portion 115, that is, the first plate-like member 11.
  • the refrigerant flowing from the first joint 31 moves from the first tank space 14 for condensation to the second tank space for condensation from the first tank space 14 for condensation. It flows toward 15 and flows into the second tank space 15 for condensation.
  • the refrigerant that has flowed into the second condensation tank space 15 flows from the second condensation tank space 15 toward the first condensation tank space 14 through the condensation part 121B located at the center in the stacking direction, and is condensed first. It flows into one tank space 14.
  • the refrigerant that has flowed into the first condensation tank space 14 flows through the condensing portion 121C on the other end side in the stacking direction from the first condensation tank space 14 toward the second condensation tank space 15 to form the first through hole.
  • 113 and the third through hole 213 flow into the gas-liquid separator 2. That is, the heat exchange unit 1 is configured such that the refrigerant flow makes a U-turn twice in the condensing unit 121.
  • the refrigerant that has flowed into the gas-liquid separation unit 2 is gas-liquid separated, and the liquid-phase refrigerant flows into the second tank space 17 for supercooling through the fourth through hole 214 and the second through hole 114.
  • the liquid-phase refrigerant that has flowed into the second supercooling tank space 17 flows from the second supercooling portion 122 toward the first supercooling tank space 16 through the second supercooling portion 122 and from the second joint 32. It flows out to the outside.
  • the condensing unit 121 is configured such that the refrigerant flow makes a U-turn twice. Thereby, since the flow velocity of the refrigerant
  • the condensing unit 121 by configuring the condensing unit 121 so that the refrigerant flow makes a U-turn twice, the high-temperature refrigerant flowing in from the discharge side of the compressor is located in the condensing unit 121 adjacent to the gas-liquid separation unit 2. There is no direct inflow. Thereby, since the refrigerant
  • the recessed part 215 is provided in the 3rd ceiling board 21A, and the clearance gap is formed between the heat exchange part 1 and the gas-liquid separation part 2.
  • the clearance gap is formed between the heat exchange part 1 and the gas-liquid separation part 2.
  • the second tank space 17 for supercooling is disposed at the lowest part in the direction of gravity. According to this, a liquid phase refrigerant with a heavy specific gravity can be flowed more reliably from the gas-liquid separation part 2.
  • the gas-liquid separation unit 2 of the present embodiment is configured by a known cylindrical modulator.
  • the gas-liquid separation unit 2 includes a main body 200, a cap 201, a filter 202, a desiccant 203, and the like.
  • the main body 200 is formed in a cylindrical shape, separates the gas-liquid of the refrigerant flowing into the inside, and stores excess refrigerant in the refrigeration cycle.
  • the main body 200 is formed of a bottomed cylindrical tank that is open at one end in the longitudinal direction.
  • the main body 200 is joined to the heat exchange unit 1 so as to open downward in the direction of gravity.
  • the cap 201 is a substantially cylindrical lid member that closes the opening of the main body 200.
  • the cap 201 can be attached to and detached from the main body 200.
  • the cap 201 is made of a compressor lubricating oil that circulates in the refrigeration cycle together with the refrigerant and a resin excellent in deterioration resistance and heat resistance with respect to the refrigerant, such as nylon and polyester.
  • the filter 202 is a member that forms a fine mesh on the whole and captures foreign matters such as dust in the refrigerant that passes through the filter 202, and is formed of the same resin material as the cap 201. Yes.
  • the desiccant 203 is one in which granular zeolite for water absorption is stored inside the bag body, and absorbs moisture in the refrigerant. This prevents each functional component constituting the refrigeration cycle from being corroded by moisture in the refrigerant, or freezing at the pores of the expansion valve to stagnate the refrigerant flow.
  • the desiccant 203 is accommodated in a space above the filter 202 in the main body 200.
  • a portion corresponding to the second tank space 15 for condensation in the first ceiling plate 11B is provided with a substantially cylindrical first protrusion 117 that protrudes toward the gas-liquid separator 2 (the other end in the stacking direction). ing.
  • a first through hole 217 is formed at a portion of the main body 200 of the gas-liquid separator 2 that faces the first protrusion 117.
  • the first through hole 217 is formed in a shape corresponding to the first projecting portion 117.
  • a first protrusion 117 is inserted into the first through hole 217.
  • the outer peripheral surface of the first protrusion 117 is directly joined to the inner peripheral surface of the first through hole 217.
  • the second tank space 15 for condensation communicates with the internal space of the main body 200 of the gas-liquid separation unit 2 via the first protrusion 117 and the first through hole 217.
  • the 1st protrusion part 117 of this embodiment has fulfill
  • the first through-hole 217 according to the present embodiment functions as a gas-liquid separation unit side inflow portion that allows the refrigerant condensed in the condensing unit 121 to flow into the gas-liquid separation unit 2. Further, as described above, the outer peripheral surface of the first protruding portion 117 is directly joined to the inner peripheral surface of the first through hole 217. Therefore, it can be said that the heat exchanger of this embodiment has the heat exchange part side outflow part and the gas-liquid separation part side inflow part directly connected without interposing other members.
  • a substantially cylindrical second protrusion 118 protruding toward the gas-liquid separator 2 (the other end side in the stacking direction). Is provided.
  • a second through hole 218 is formed in a portion of the main body 200 of the gas-liquid separator 2 that faces the second protrusion 118.
  • the second through hole 218 is formed in a shape corresponding to the second protrusion 118.
  • a second protrusion 118 is inserted into the second through hole 218.
  • the outer peripheral surface of the second protrusion 118 is directly joined to the inner peripheral surface of the second through hole 218.
  • the second through-hole 218 of the present embodiment functions as a gas-liquid separation part side outflow part that causes the liquid-phase refrigerant separated in the gas-liquid separation part 2 to flow out.
  • the second projecting portion 118 of the present embodiment functions as a heat exchange portion side inflow portion that causes the liquid-phase refrigerant separated in the gas-liquid separation portion 2 to flow into the subcooling portion 122.
  • the outer peripheral surface of the second protrusion 118 is directly joined to the inner peripheral surface of the second through hole 218. Therefore, it can be said that the heat exchanger of this embodiment has the heat exchange part side inflow part and the gas-liquid separation part side outflow part directly connected without interposing other members.
  • the first protrusion 117 and the second protrusion 118 are formed integrally with the first ceiling plate 11B.
  • the 1st protrusion part 117 and the 2nd protrusion part 118 are formed by giving a burring process to the 1st ceiling board 11B.
  • the condensing part 121 and the supercooling part 122 are provided side by side in the arrangement direction in the refrigerant passage 12 formed between the first plate-like members 11. .
  • an existing modulator mass product
  • the fifth embodiment is different from the first embodiment in the configuration of the portion where the heat exchange unit 1 and the gas-liquid separation unit 2 are joined.
  • the arrangement direction of the condensing unit 121 and the supercooling unit 122 coincides with the horizontal direction.
  • the width direction coincides with the gravity direction.
  • the third ceiling plate 21 ⁇ / b> A located closest to the heat exchange unit 1 is the other second plate member 21 ⁇ / b> A.
  • the plate thickness is thicker.
  • the plate-shaped coupling member 25 is arrange
  • the coupling member 25 is joined to the third ceiling plate 21A by brazing.
  • the coupling member 25 is provided with a plurality of protrusions 251 (first protrusions) that partially protrude toward the first ceiling plate 11B.
  • the protrusion 251 is joined to the first ceiling plate 11B by brazing.
  • a gap is formed between the first ceiling plate 11 ⁇ / b> B and the third ceiling plate 21 ⁇ / b> A, that is, between the heat exchange unit 1 and the gas-liquid separation unit 2. be able to.
  • This gap is an air layer in which air is present, and serves as a heat insulating part between the heat exchange part 1 and the gas-liquid separation part 2.
  • one protrusion 251 is disposed at a portion corresponding to the first through hole 113.
  • a first communication hole 252 communicating with the first through hole 113 is formed in the protrusion 251 corresponding to the first through hole 113.
  • the condensation second tank space 15 communicates with the gas-liquid separation passage 22 via the first through hole 113 and the first communication hole 252.
  • the protruding portion 251 functions as a partition that partitions the refrigerant flow path between the second tank space 15 for condensation and the gas-liquid separation passage 22 and the heat insulating air layer between the heat exchange portion 1 and the gas-liquid separation portion 2. Plays.
  • the other one of the plurality of protrusions 251 is disposed at a portion corresponding to the second through hole 114.
  • the protrusion 251 corresponding to the second through hole 114 has the same structure as the protrusion 251 corresponding to the first through hole 113 shown in FIG. Therefore, the reference numerals corresponding to the structure in the vicinity of the second through hole 114 are given in parentheses in FIG.
  • a second communication hole 253 that communicates with the second through hole 114 is formed in the projecting portion 251 corresponding to the first through hole 113.
  • the supercooling first tank space 16 communicates with the gas-liquid separation passage 22 via the second through hole 114 and the second communication hole 253.
  • the projecting portion 251 is a partition wall that partitions the refrigerant flow path between the first tank space 16 for supercooling and the gas-liquid separation passage 22 and the adiabatic air layer between the heat exchange portion 1 and the gas-liquid separation portion 2. Playing a role.
  • the second ceiling plate 21B located on the outermost side on the other end side in the stacking direction and the outermost 2 on the other end side in the stacking direction
  • the fourth fourth ceiling plate 21 ⁇ / b> C is thicker than the other second plate-like members 21. Thereby, the gas-liquid separation part 2 is reinforced.
  • the inner fin 26 is joined to the surface on the one end side in the stacking direction of the second ceiling plate 21B and the fourth ceiling plate 21C by brazing.
  • the inner fin 26 is a reinforcing member that reinforces the gas-liquid separator 2.
  • a collar 27 is disposed between the second plate members 21 other than the second ceiling plate 21B and the fourth ceiling plate 21C among the multiple second plate members 21 constituting the gas-liquid separation unit 2. ing.
  • the collar 27 is a reinforcing member that reinforces the gas-liquid separator 2.
  • the collar 27 is joined to both of the second plate-like members 21 adjacent to each other by brazing.
  • the collar 27 has a cylindrical portion, and is arranged at the periphery of the through hole 219 provided in the second plate member 21.
  • the through hole 219 is a communication hole that allows adjacent gas-liquid separation passages 22 to communicate with each other.
  • the cylindrical portion of the collar 27 is provided with at least one notch. Thereby, the collar 27 does not disturb the communication between the adjacent gas-liquid separation passages 22.
  • a plate-like coupling member 25 interposed between the heat exchange unit 1 and the gas-liquid separation unit 2 is provided.
  • the coupling member 25 couples the heat exchange unit 1 and the gas-liquid separation unit 2, and forms a gap where air exists between the heat exchange unit 1 and the gas-liquid separation unit 2. Thereby, the heat insulation between the heat exchange part 1 and the gas-liquid separation part 2 can be improved.
  • the coupling member 25 has a protruding portion 251 that protrudes from one of the heat exchange unit 1 and the gas-liquid separation unit 2 toward the other to form a gap. Thereby, a clearance gap can be formed between the heat exchange part 1 and the gas-liquid separation part 2 by simple structure.
  • the projecting portion 251 is formed with communication holes 252 and 253 that allow the refrigerant passage 12 and the internal space of the gas-liquid separation portion 2 to communicate with each other.
  • a clearance gap is formed between the heat exchange part 1 and the gas-liquid separation part 2, and the refrigerant path 12 and the internal space of the gas-liquid separation part 2 can be communicated.
  • the supercooling side inner fins 52 are not limited thereto.
  • an offset fin in which wall portions 52a dividing the supercooling side narrow channel 122a are arranged in a staggered manner along the refrigerant flow direction may be adopted. According to this, it is possible to share the condensing side inner fin 51 and reduce the dead water region due to the refrigerant diffusibility of the inner fin.
  • the arrangement direction may be arranged so that the stacking direction matches the horizontal direction.
  • a solid line arrow indicates a cooling water flow
  • a broken line arrow indicates a refrigerant flow.
  • a desiccant may be provided inside the gas-liquid separation unit 2.
  • a desiccant insertion hole is set on the outer side of the gas-liquid separator 2 (the other end in the stacking direction, for example, the second ceiling plate 21B), and the lid is covered with a plug or the like after the desiccant is inserted.
  • a desiccant may be provided inside the separation unit 2.
  • the coupling member 25 is provided with the protrusion 251 so that a gap is formed between the heat exchange unit 1 and the gas-liquid separation unit 2, but the coupling member 25 is notched.
  • a gap may be formed between the heat exchange unit 1 and the gas-liquid separation unit 2 by providing a hole or a hole.
  • the heat insulating part 123 that insulates the condensing part 121 and the supercooling part 122 is arranged between the condensing part 121 and the supercooling part 122 in the refrigerant passage 12.
  • At least one first plate-like member 11 of the two first plate-like members 11 forming the cooling water passage 13 is directed toward the other first plate-like member 11 facing one first plate-like member 11.
  • the protrusion part which protrudes in this way is formed, and the condensation part 121 and the supercooling part 122 are separated and insulated by the protrusion part.
  • the protruding portion has a shape in which the surface of the first plate member 11 facing the cooling water passage 13 is recessed toward the coolant passage 12, and the recessed portion communicates with the cooling water passage 13. That's fine.

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

Abstract

L'invention concerne un échangeur thermique empilé comportant une section d'échange thermique (1) et une section de séparation gaz-liquide (2). La section d'échange thermique échange la chaleur entre le réfrigérant d'un cycle de réfrigération et un milieu thermique. La section de séparation gaz-liquide sépare les composants gazeux et liquides d'un réfrigérant qui s'est écoulé dans la section de séparation gaz-liquide. La section d'échange thermique est formée par empilement et raccordement d'une pluralité de premiers éléments en forme de plaque (11). Une pluralité de passages de réfrigérant (12) à travers lesquels s'écoule le réfrigérant et une pluralité de passages d'écoulement de milieu thermique (13) à travers lesquels s'écoule un milieu thermique est formée entre la pluralité de premiers éléments en forme de plaque. La pluralité de passages de réfrigérant et la pluralité de passages d'écoulement de milieu thermique sont disposées l'une à côté de l'autre dans la direction d'empilement de la pluralité de premiers éléments en forme de plaque. Dans les passages de réfrigérant, on a disposé : des sections de condensation (121) destinées à un échange de chaleur entre un réfrigérant en phase gazeuse et le milieu thermique pour condenser le réfrigérant en phase gazeuse ; et des sections de surfusion (122) destinées à la surfusion d'un réfrigérant en phase liquide par échange de chaleur entre un milieu thermique et un réfrigérant en phase liquide, obtenu par séparation gaz-liquide dans la section de séparation gaz-liquide, les sections de condensation (121) et les sections de surfusion (122) étant disposées les unes à côté des autres dans la direction perpendiculaire à la direction d'empilement. Dans les passages de réfrigérant, les sections de condensation et les sections de surfusion sont séparées par des sections d'isolation thermique (123).
PCT/JP2015/005262 2014-10-30 2015-10-19 Échangeur thermique empilé WO2016067551A1 (fr)

Priority Applications (1)

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DE112015004908.8T DE112015004908T5 (de) 2014-10-30 2015-10-19 Gestapelter Wärmetauscher

Applications Claiming Priority (4)

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JP2014-221498 2014-10-30
JP2014221498 2014-10-30
JP2015154477A JP6497262B2 (ja) 2014-10-30 2015-08-04 積層型熱交換器
JP2015-154477 2015-08-04

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WO2016067551A1 true WO2016067551A1 (fr) 2016-05-06

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019039663A (ja) * 2017-08-28 2019-03-14 ハンオン システムズ 凝縮器
CN114945781A (zh) * 2020-01-30 2022-08-26 舒瑞普国际股份公司 制冷系统和方法

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10132476A (ja) * 1996-10-28 1998-05-22 Daikin Ind Ltd プレート式熱交換器
JP2002022374A (ja) * 2000-07-07 2002-01-23 Hitachi Ltd プレート式熱交換器および冷凍空調装置
JP2004197984A (ja) * 2002-12-17 2004-07-15 Toyo Radiator Co Ltd 一体型多板式熱交換器

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10132476A (ja) * 1996-10-28 1998-05-22 Daikin Ind Ltd プレート式熱交換器
JP2002022374A (ja) * 2000-07-07 2002-01-23 Hitachi Ltd プレート式熱交換器および冷凍空調装置
JP2004197984A (ja) * 2002-12-17 2004-07-15 Toyo Radiator Co Ltd 一体型多板式熱交換器

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019039663A (ja) * 2017-08-28 2019-03-14 ハンオン システムズ 凝縮器
CN114945781A (zh) * 2020-01-30 2022-08-26 舒瑞普国际股份公司 制冷系统和方法

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