WO2017195588A1 - Échangeur de chaleur de type à empilage - Google Patents

Échangeur de chaleur de type à empilage Download PDF

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Publication number
WO2017195588A1
WO2017195588A1 PCT/JP2017/016318 JP2017016318W WO2017195588A1 WO 2017195588 A1 WO2017195588 A1 WO 2017195588A1 JP 2017016318 W JP2017016318 W JP 2017016318W WO 2017195588 A1 WO2017195588 A1 WO 2017195588A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
fluid
passage
plate
cooling water
Prior art date
Application number
PCT/JP2017/016318
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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
Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Priority to CN201780021887.4A priority Critical patent/CN109073337A/zh
Publication of WO2017195588A1 publication Critical patent/WO2017195588A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • 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
    • F25B39/02—Evaporators
    • 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

  • This disclosure relates to a stacked heat exchanger.
  • Patent Document 1 discloses that a U-turn flow is employed in order to increase heat exchange efficiency.
  • the partition portion of the fluid passage is formed by ribs formed on the plate.
  • This disclosure aims to improve brazing performance in a laminated heat exchanger having a U-turn flow structure.
  • the stacked heat exchanger includes a heat exchange unit that exchanges heat between the first fluid and the second fluid.
  • the heat exchange part is formed by laminating and joining a plurality of plate-like members.
  • a plurality of first fluid passages through which the first fluid flows and a plurality of second fluid passages through which the second fluid flows are formed between the plurality of plate-like members.
  • the plurality of first fluid passages and the plurality of second fluid passages are arranged side by side in the stacking direction of the plurality of plate-like members.
  • the first fluid passage and the second fluid passage have an upstream passage and a downstream passage, and the first fluid or the second fluid that flows through the upstream passage makes a U-turn and can flow through the downstream passage.
  • Inner fins that join adjacent plate-like members and promote heat exchange between the first fluid and the second fluid are disposed in the first fluid passage and the second fluid passage.
  • a partition for partitioning the upstream passage and the downstream passage is formed by an inner fin.
  • the partition part formed by the inner fin can be utilized as a heat radiation area, the heat exchange performance of the partition part can be improved.
  • the partition portion by forming the partition portion with the inner fin, it is possible to improve the brazing property and improve the pressure resistance.
  • a plurality of plate-like members and a plurality of inner fins are laminated, and brazing is performed in a state where these are compressed.
  • the plate-like member is less likely to be lifted and the occurrence of poor brazing can be suppressed compared to the configuration in which the ribs formed on the plate-like member are joined to each other. it can.
  • the number of brazing starting points is increased and the brazing property is improved.
  • FIG. 3 is a sectional view taken along line III-III in FIG.
  • a heat exchanger 10 shown in FIG. 1 constitutes a refrigeration cycle of a vehicle air conditioner.
  • the heat exchanger 10 is configured as a chiller that cools the cooling water by exchanging heat between the low-pressure refrigerant of the refrigeration cycle and the cooling water.
  • the refrigerant in the refrigeration cycle corresponds to the first fluid of the present disclosure
  • the cooling water corresponds to the second fluid 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 1 forms a refrigerant path and a heat medium path alternately between the heat transfer plates by overlapping a plurality of substantially flat plate heat transfer plates at intervals, thereby This is a stacked heat exchanger for heat exchange.
  • the heat exchanger 1 includes a heat exchanging unit 10 for exchanging heat between the refrigerant of the refrigeration cycle and the cooling water.
  • the heat exchange unit 10 is integrally formed by laminating and joining a plurality of plate-like members 11.
  • the plate-like member 11 is an elongated, substantially rectangular plate material.
  • a specific material for example, a double-sided clad material in which a brazing material is clad on both surfaces of an aluminum core material is used.
  • the stacking direction of the first plate-like members 11 (vertical direction in the example of FIG. 1) is referred to as a plate stacking direction.
  • the direction in which the short side extends is the short direction (the vertical direction in FIGS. 2, 4, and 5), and the direction in which the long side extends is the longitudinal direction (FIGS. 2, 4). In FIG. 5, the horizontal direction).
  • an overhanging portion 11 a that protrudes in a substantially plate stacking direction (in other words, a direction substantially orthogonal to the plate surface of the plate-like member 11) is formed.
  • the plurality of plate-like members 11 are joined to each other by brazing, with the overhanging portions 11a being laminated.
  • 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 plate-like members 11.
  • the refrigerant passage 12 corresponds to the first fluid passage of the present disclosure
  • the cooling water passage 13 corresponds to the second fluid passage of the present disclosure.
  • the refrigerant passage 12 and the cooling water passage 13 are also referred to as fluid passages 12 and 13.
  • the plurality of refrigerant passages 12 and the plurality of cooling water passages 13 are arranged side by side in the plate stacking direction. More specifically, the refrigerant passages 12 and the cooling water passages 13 are alternately stacked (parallelly arranged) one by one in the plate stacking direction.
  • the 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 plate-like member 11.
  • the refrigerant passage 12 is disposed on the outermost side in the stacking direction.
  • the heat exchanging unit 10 includes a first refrigerant tank space 14, a second refrigerant tank space 15, a first cooling water tank space 16, and a second cooling water tank space 17. It has.
  • the plate-like member 11 has the first refrigerant tank space 14, the second refrigerant tank space 15, the first coolant tank space 16, and the second coolant water in addition to the fluid passages 12 and 13 described above.
  • a tank space 17 is formed.
  • refrigerant tank spaces 14 and 15 are provided on one end side in the longitudinal direction of the plate-like member 11 (left side in the example of FIG. 1), and on the other end side (right side in the example of FIG. 1). Cooling water tank spaces 16 and 17 are provided.
  • the first refrigerant tank space 14 and the second refrigerant tank space 15 distribute and collect the refrigerant with respect to the plurality of refrigerant passages 12.
  • the first cooling water tank space 16 and the second cooling water tank space 17 distribute and collect cooling water to the plurality of cooling water passages 13.
  • the first refrigerant tank space 14 distributes the refrigerant to the plurality of refrigerant passages 12.
  • the second refrigerant tank space 15 collects refrigerant with respect to the plurality of refrigerant passages 12.
  • the first cooling water tank space 16 distributes the cooling water to the plurality of cooling water passages 13.
  • the second cooling water tank space 17 collects cooling water for the plurality of cooling water passages 13.
  • refrigerant ports 11 b and 11 c and cooling water ports 11 d and 11 e are formed as openings at the four corners of the plate-like member 11 (four corners at the top, bottom, left and right in the examples of FIGS. 4 and 5). ing.
  • the inlet side refrigerant port 11b forms a first refrigerant tank space 14
  • the outlet side refrigerant port 11c forms a second refrigerant tank space 15
  • the inlet side cooling water port 11d forms a first cooling water tank space 16.
  • the second cooling water tank space 17 is configured by the outlet side cooling water port 11e.
  • the inlet-side refrigerant port 11b corresponds to the inlet-side opening of the present disclosure
  • the outlet-side refrigerant port 11c corresponds to the outlet-side opening of the present disclosure.
  • the heat exchanger 1 is provided with a refrigerant inflow portion 18, a refrigerant outflow portion 19, a cooling water inflow portion 20, and a cooling water outflow portion 21.
  • the refrigerant inflow portion 18 communicates with the first refrigerant tank space 14, and the refrigerant outflow portion 19 communicates with the second refrigerant tank space 15.
  • the cooling water inflow portion 20 communicates with the first cooling water tank space 16, and the cooling water outflow portion 21 communicates with the second cooling water tank space 17.
  • the refrigerant inflow portion 18 and the refrigerant outflow portion 19 are arranged at the end of the plate member 11 on the same side in the longitudinal direction (left side in the example of FIG. 2).
  • the refrigerant inflow portion 18 and the refrigerant outflow portion 19 are arranged adjacent to each other in the short direction of the plate-like member 11. As shown in FIG. 2, in the present embodiment, the refrigerant outflow portion 19 is disposed above the refrigerant inflow portion 18.
  • the cooling water inflow portion 20 and the cooling water outflow portion 21 are arranged at the end of the plate-like member 11 on the same side in the longitudinal direction (right side in the example of FIG. 2).
  • the cooling water inflow portion 20 and the cooling water outflow portion 21 are disposed at opposite ends of the plate-like member 11 in the longitudinal direction with respect to the refrigerant inflow portion 18 and the refrigerant outflow portion 19.
  • the cooling water inflow portion 20 and the cooling water outflow portion 21 are arranged adjacent to each other in the lateral direction of the plate member 11.
  • An expansion valve 22 is provided in the refrigerant inflow portion 18 and the refrigerant outflow portion 19.
  • the expansion valve 22 of the present embodiment is a temperature type expansion valve, and is configured to adjust the throttle passage area by a mechanical mechanism so that the degree of superheat of the outlet side refrigerant falls within a predetermined range.
  • the expansion valve 22 includes a decompression section 22a for decompressing and expanding the refrigerant, and a temperature sensing section 22b having a displacement member (diaphragm) that is displaced according to the temperature and pressure of the outlet side refrigerant.
  • the decompression unit 22a and the temperature sensing unit 22b are integrated.
  • the decompression part 22 a of the expansion valve 22 is arranged on the refrigerant inflow part 18 side, and decompresses the refrigerant flowing into the refrigerant inflow part 18.
  • the temperature sensing part 22b of the expansion valve 22 is arranged on the refrigerant outflow part 19 side, and the displacement member is displaced according to the temperature and pressure of the outlet side refrigerant.
  • the valve opening degree (refrigerant flow rate) of the decompression unit 22a is adjusted according to the displacement of the displacement member in the temperature sensing unit 22b.
  • the temperature sensitive portion 22 b is configured based on the temperature of the outlet side refrigerant without using external piping.
  • the valve opening degree of the pressure reduction part 22a can be adjusted by operating.
  • inner fins 30 and 40 are arranged in fluid passages 12 and 13 formed between the plate-like members 11. These inner fins 30 and 40 are interposed between the plate-like members 11 and divide the refrigerant passage 12 or the cooling water passage 13 into a plurality of narrow flow passages 12a and 13a so that the refrigerant and the cooling water are separated. It is a heat exchange promoting member that promotes heat exchange.
  • inner fins 30 and 40 As a specific material of the inner fins 30 and 40, for example, a double-sided clad material in which a brazing material is clad on both sides of an aluminum core is used. Inner fins 30 and 40 are joined to both adjacent plate-like members 11 by brazing. Therefore, the inner fins 30 and 40 constitute an inner wall that joins adjacent plate-like members 11 and crosses the refrigerant passage 12 and the cooling water passage 13 in the stacking direction.
  • the refrigerant-side inner fin 30 is provided in the entire refrigerant passage 12.
  • the refrigerant side inner fin 30 is also provided around the refrigerant ports 11b and 11c and the cooling water ports 11d and 11e formed at the end of the plate-like member 11. For this reason, the plate-shaped member 11 is joined via the inner fin 30 also around the refrigerant ports 11b and 11c and the cooling water ports 11d and 11e.
  • the refrigerant-side inner fin 30 has a main flow portion 31 and a partition portion 32.
  • the main flow portion 31 occupies most of the refrigerant side inner fin 30.
  • the partition 32 has a role of partitioning the refrigerant passage 12 and circulating the refrigerant in a U-turn.
  • the mainstream portion 31 is configured as an offset fin.
  • the offset fin has a wave shape in which the wall portion 31 a and the top portion 31 b are continuous, and a corrugated cross-sectional shape is formed in the wave continuous direction.
  • the offset fin is formed, for example, by pressing a plurality of punches on a flat plate and bending it.
  • the plurality of wall portions 31a and the plurality of top portions 31b are provided in parallel.
  • the plurality of top portions 31b extend along the refrigerant flow direction F, respectively.
  • the wall portion 31a is provided with a number of cut and raised portions 31c that are partially cut and raised.
  • the wall portions 31a and the cut-and-raised portions 31c are alternately arranged in a staggered manner along the refrigerant flow direction F.
  • a large number of slit holes are formed in the wall portion 31a of the offset fin by the cut-and-raised portion 31c, and adjacent narrow channels 12a defined by the wall portion 31a communicate with each other. For this reason, in the mainstream portion 31, the refrigerant flows while diffusing.
  • the partition 32 is configured as a straight fin. As shown in FIG. 7, the straight fin has a wave shape in which the wall portion 32 a and the top portion 32 b are continuous, and a corrugated cross-sectional shape is formed in the wave continuous direction.
  • the plurality of wall portions 32a and the plurality of top portions 32b are respectively provided in parallel.
  • the plurality of wall portions 32a and the plurality of top portions 32b extend linearly along the refrigerant flow direction F, respectively.
  • the refrigerant passage 12 is partitioned into a plurality of narrow channels 12a by the wall portion 32a.
  • no slit hole is formed in the wall portion 32a, and the adjacent narrow channel 12a defined by the wall portion 32a is not communicated.
  • the partition part 32 it distribute
  • the partition part 32 is provided so that it may extend along the longitudinal direction (left-right direction in the example of FIG. 4) of the plate-shaped member 11.
  • the refrigerant passage 12 is divided into an upstream refrigerant passage 12b and a downstream refrigerant passage 12c by a partition 32.
  • the upstream refrigerant passage 12b corresponds to the upstream passage of the present disclosure
  • the downstream refrigerant passage 12c corresponds to the downstream passage of the present disclosure.
  • the partition 32 is provided up to the end of the refrigerant passage 12 on the refrigerant ports 11b and 11c side (left side in the example of FIG. 4).
  • the partition part 32 is provided between the inlet-side refrigerant port 11b and the outlet-side refrigerant port 11c. For this reason, the refrigerant cannot flow from the inlet side refrigerant port 11b to the outlet side refrigerant port 11c in the shortest distance.
  • the end portions of the partition portion 32 on the refrigerant ports 11b and 11c side extend to the wall surface of the overhang portion 11a. For this reason, the refrigerant
  • the partition 32 is provided on the cooling water port 11d, 11e side of the refrigerant passage 12 (on the right side in the example of FIG. 4) up to the front of the cooling water ports 11d, 11e. That is, when viewed from the short side of the plate-like member 11, the partition portion 32 and the cooling water ports 11d and 11e are separated by a predetermined distance.
  • the portion of the refrigerant passage 12 where the partition portion 32 is not provided is a refrigerant U-turn portion 12d that changes the flow direction of the refrigerant.
  • the refrigerant U-turn part 12d the refrigerant flows while diffusing through the main flow part 31, so that the flow direction can be changed.
  • the edge part by the side of the cooling water ports 11d and 11e in the partition part 32 is connected to the refrigerant path 12, and a refrigerant
  • a communicating portion 33 is provided in the vicinity of the outlet side refrigerant port 11 c in the partition portion 32.
  • the communication part 33 is formed by cutting out the wall part 32a of the partition part 32, and connects the adjacent narrow flow paths 12a partitioned by the wall part 32a.
  • the communication part 33 is provided in the outlet side refrigerant port 11 c in the partition part 32. For this reason, the narrow channel 12a in the partition 32 can be communicated with the downstream portion of the downstream refrigerant passage 12c in the refrigerant flow direction, specifically, in the vicinity of the outlet side refrigerant port 11c by the communication portion 33.
  • the offset fins constituting the main flow part 31 and the straight fins constituting the partition part 32 may be integrated or separated.
  • the main flow portion 31 and the partition portion 32 are integrated.
  • the work of arranging the refrigerant-side inner fins 30 on the plate-like member 11 becomes easy, and the work man-hours can be reduced.
  • the refrigerant-side inner fin 30 may be formed in a pseudo straight fin shape by cutting the raised portion 31c at a portion corresponding to the partition portion 32 in an offset fin processing step, for example.
  • the straight fin shape and the offset fin shape may be combined by combining a range in which the cut and raised portion 31c is formed and a range in which the cut and raised portion 31c is not formed.
  • the refrigerant flows through the narrow flow path 12 a defined by the main flow portion 31 of the refrigerant-side inner fin 30.
  • the refrigerant changes the flow direction at the refrigerant U-turn portion 12d and flows through the downstream refrigerant passage 12c.
  • the refrigerant also flows into the partition part 32 from the refrigerant U-turn part 12d and flows through the narrow flow path 12a in the partition part 32.
  • the refrigerant flowing through the partition 32 joins the downstream refrigerant passage 12c at the communication portion 33, and then flows out into the second refrigerant tank space 15.
  • the cooling water side inner fin 40 is provided in the entire cooling water passage 13.
  • the cooling water side inner fin 40 is also provided around the refrigerant ports 11 b and 11 c and the cooling water ports 11 d and 11 e formed at the end of the plate-like member 11.
  • the cooling water side inner fin 40 includes a main flow portion 41, a partition portion 42, and a communication portion 43.
  • the main flow portion 41, the partition portion 42, and the communication portion 43 of the cooling water side inner fin 40 have the same configuration as the main flow portion 31, the partition portion 32, and the communication portion 33 of the refrigerant side inner fin 30, respectively. Detailed description is omitted.
  • the cooling water passage 13 is divided into an upstream side cooling water passage 13b and a downstream side cooling water passage 13c by a partitioning portion 42, and the cooling water flows through a portion of the cooling water passage 13 where the partitioning portion 42 is not provided. It becomes the cooling water U-turn part 13d which changes a direction.
  • the upstream side cooling water passage 13b corresponds to the upstream side passage of the present disclosure
  • the downstream side cooling water passage 13c corresponds to the downstream side passage of the present disclosure.
  • the cooling water that has flowed into the cooling water passage 13 from the first cooling water tank space 16 flows through the upstream cooling water passage 13 b along the partition portion 42 of the cooling water-side inner fin 40.
  • the cooling water flows through the narrow flow path 13 a defined by the main flow portion 41 of the cooling water side inner fin 40.
  • the cooling water changes the flow direction at the cooling water U-turn portion 13d and flows through the downstream cooling water passage 13c.
  • the cooling water that has flowed through the downstream cooling water passage 13 c flows out into the second cooling water tank space 17.
  • the cooling water also flows into the partition part 42 from the cooling water U-turn part 13d and flows through the narrow flow path 13a in the partition part 42.
  • the cooling water that has circulated through the partition 42 joins the downstream cooling water passage 13 c at the communication portion 43 and then flows out into the second cooling water tank space 17.
  • a joint portion 11f is provided around the refrigerant ports 11b and 11c.
  • the joining portion 11f is a joint that joins the plate surfaces of the adjacent plate-like members 11 together.
  • the joining portion 11f is configured so that the plate surface around the refrigerant ports 11b and 11c in the plate-like member 11 is a cooling water flow path with respect to the main surface of the plate-like member 11 (that is, the surface on which the refrigerant-side inner fin 30 is disposed). It is formed by offsetting to the 13 side.
  • the joining portion 11f is offset to the vicinity of the center of the cooling water passage 13 formed between the adjacent plate-like members 11.
  • the joining portions 11f of the two adjacent plate-like members 11 are joined by brazing between the opposing plate surfaces. That is, the joint part 11f of the two plate-like members 11 adjacent to each other with the cooling water passage 13 interposed therebetween is a face-to-face joint. According to such a configuration, the pressure resistance in the vicinity of the refrigerant ports 11b and 11c can be improved.
  • FIG. 8 shows the stress generated around the refrigerant ports 11b and 11c when the internal pressure of the heat exchanger 1 is increased by the refrigerant.
  • FIG. 8 shows the stress analysis results of the heat exchanger 1 of the present embodiment and the heat exchanger of the comparative example. The stress analysis shown in FIG. 8 was performed assuming that the heat exchanger 1 is elastically deformed.
  • Comparative Examples 1 and 2 of the two plate-like members 11 constituting the cooling water passage 13, the joint 11f of one plate-like member 11 is not offset, and the joint 11f of the other plate-like member 11 is not offset. It was set as the structure offset to the plate
  • FIG. Comparative Example 1 is a plate-like member positioned on the lower side of the two plate-like members 11 constituting the cooling water passage 13 without offsetting the joint portion 11f of the plate-like member 11 located on the upper side in FIG. Only the 11 joints 11f were offset.
  • the two plate-like members 11 constituting the cooling water passage 13 are offset by only the joint portion 11f of the plate-like member 11 located on the upper side in FIG. 11 joints 11f are not offset.
  • Comparative Example 3 reinforcing ribs projecting toward the refrigerant passage 12 are formed around the refrigerant ports 11b and 11c, and the reinforcing ribs of the two plate-like members 11 are joined to each other. Furthermore, in the comparative example 3, it is set as the burring joint which carried out the burring process around the refrigerant openings 11b and 11c, and joined the burring processed plate surfaces.
  • the plate-like members 11 are joined to each other around the refrigerant ports 11 b and 11 c via the inner fins 30 and 40. Since the inner fins 30 and 40 are uniformly arranged in the fluid passages 12 and 13, the stress generated around the refrigerant port 11f is dispersed by the inner fins 30 and 40. Furthermore, in this embodiment, even if the internal pressure of the refrigerant passage 12 rises and the refrigerant side inner fin 30 is deformed by offsetting the joint portion 11f near the center of the cooling water passage 13, the deformation load is reduced. The influence can be minimized. For this reason, according to the structure of this embodiment, generated stress can be reduced and pressure
  • the partition portions 32 and 42 of the U-turn flow are formed by the inner fins 30 and 40 provided in the fluid passages 12 and 13.
  • the partition parts 32 and 42 can be utilized as a thermal radiation area
  • brazing property can be improved by forming the partition parts 32 and 42 by the inner fins 30 and 40.
  • FIG. In the laminated heat exchanger, a plurality of plate-like members 11 and a plurality of inner fins 30 and 40 are laminated, and brazing is performed in a state where these are compressed.
  • the plate-like member 11 is less likely to be lifted, compared to the configuration in which the ribs formed on the plate-like member 11 are joined together. The occurrence of improper attachment can be suppressed.
  • the brazing start point is increased and the brazing property is improved.
  • the partition portions 32 and 42 are provided with communication portions 33 and 43 that allow the narrow flow channels 12a and 13a formed therein to communicate with the outlet-side refrigerant port 11c or the outlet-side cooling water port 11e. .
  • the fluid that has passed through the insides of the partition parts 32 and 42 can flow out to the outside of the partition parts 32 and 42.
  • the pressure loss of the fluid in the partition parts 32 and 42 can be reduced.
  • the inlet side refrigerant port 11b and the outlet side refrigerant port 11c are arranged side by side in the lateral direction of the plate-like member 11, and a partition is formed between the inlet side refrigerant port 11b and the outlet side refrigerant port 11c.
  • a part 32 is provided.
  • the refrigerant flows directly from the inlet side refrigerant port 11b to the outlet side refrigerant port 11c, or a circulation flow such as the inlet side refrigerant port 11b ⁇ the upstream side refrigerant passage 12b ⁇ the partition portion 32 ⁇ the inlet side refrigerant port 11b is generated. It is possible to prevent this, and the effect of partitioning the refrigerant by the partition portion 32 can be enhanced.
  • the same effect can be obtained by the partition portion 42 also in the cooling water ports 11 d and 11 e of the cooling water passage 13.
  • the main fins 31 and 41 of the inner fins 30 and 40 are offset fins through which fluid can flow while diffusing.
  • the inner fins 30 and 40 can be arranged around the U-turn portions 12d and 13d where the fluid makes a U-turn, the refrigerant ports 11b and 11c, and the cooling water ports 11d and 11e. Can be used as As a result, the heat radiation area of the inner fins 30 and 40 can be increased and the heat exchange performance can be improved.
  • the inner fins 30 and 40 are disposed around the refrigerant ports 11b and 11c, and the joint portion 11f provided around the refrigerant ports 11b and 11c is offset toward the cooling water passage 13 side.
  • the pressure resistance is improved.
  • the plurality of plate-like members 11 and the plurality of inner fins 30, 40 are stacked by joining the plate-like members 11 around the refrigerant ports 11 b, 11 c via the inner fins 30, 40.
  • the plate-like member 11 is hardly lifted, and coupled with an increase in the starting point of brazing, it is possible to suppress the occurrence of poor brazing.
  • the inner fins 30 and 40 are uniformly arranged between the plate-like members 11, when the internal pressure of the heat exchange unit 10 becomes high, the stress generated around the refrigerant ports 11b and 11c is generated. Easy to disperse.
  • the pressure resistance around the refrigerant ports 11b and 11c can be improved. Therefore, in the U-turn flow structure, the refrigerant port inflow portion 18 and the refrigerant outflow portion 19 are arranged in the short direction of the plate-like member 11. It becomes possible to arrange them side by side. Thereby, the decompression part 22a and the temperature sensing part 22b can be integrated without using external piping by providing the decompression part 22a in the refrigerant inflow part 18 and providing the temperature sensing part 22b in the refrigerant outflow part 19.
  • the present invention is not limited thereto, and the stacked heat exchanger of the present disclosure exchanges heat between, for example, a high-pressure refrigerant and cooling water in a refrigeration cycle. It is also possible to apply to a condenser that cools the refrigerant.
  • the first fluid is the refrigerant of the refrigeration cycle and the second fluid is the cooling water, but the first fluid and the second fluid are not limited to these.
  • the partition parts 32 and 42 formed in the inner fins 30 and 40 were comprised as a straight fin from which the wall parts 32a and 42a extended linearly, not only this but the partition parts 32 and 42 are set as a different structure. Also good.
  • the wall portions 32a and 42a may be configured to meander.

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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)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

La présente invention concerne un échangeur de chaleur de type à empilage pourvu d'une section d'échange de chaleur (10) pour échanger de la chaleur entre un premier fluide et un deuxième fluide. La section d'échange de chaleur est formée par empilage et assemblage d'une pluralité d'éléments en forme de plaque (11). Une pluralité de premiers passages de fluide (12) à travers lesquels le premier fluide s'écoule et une pluralité de deuxièmes passages de fluide (13) à travers lesquels le deuxième fluide s'écoule sont formés entre la pluralité d'éléments en forme de plaque. La pluralité de premiers passages de fluide et la pluralité de deuxièmes passages de fluide sont agencés les uns à côté des autres dans la direction dans laquelle la pluralité d'éléments en forme de plaque sont empilés. Les premier et deuxième passages d'écoulement comportent des passages supérieurs (12b, 13b) et des passages inférieurs (12c, 13c) et sont configurés de sorte que le premier fluide ou le deuxième fluide ayant circulé à travers les passages supérieurs peut faire demi-tour et s'écouler à travers les passages inférieurs. Des ailettes internes (30, 40) sont agencées dans les premier et deuxième passages de fluide, les ailettes internes (30, 40) reliant les éléments en forme de plaque adjacents et favorisant l'échange de chaleur entre le premier fluide et le deuxième fluide. Des cloisons (32, 42) pour séparer les passages supérieurs et les passages inférieurs sont formées par les ailettes internes.
PCT/JP2017/016318 2016-05-13 2017-04-25 Échangeur de chaleur de type à empilage WO2017195588A1 (fr)

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CN201780021887.4A CN109073337A (zh) 2016-05-13 2017-04-25 层叠型热交换器

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JP2016097289A JP2017203613A (ja) 2016-05-13 2016-05-13 積層型熱交換器
JP2016-097289 2016-05-13

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Publication number Priority date Publication date Assignee Title
CN110375573A (zh) * 2019-08-07 2019-10-25 浙江银轮机械股份有限公司 芯片组件及冷却器
JP2021085535A (ja) * 2019-11-25 2021-06-03 ダイキン工業株式会社 熱交換器

Citations (7)

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JPS637723U (fr) * 1986-06-30 1988-01-19
JPH0417263U (fr) * 1990-05-25 1992-02-13
JPH06123581A (ja) * 1992-10-09 1994-05-06 Mitsubishi Heavy Ind Ltd 積層型熱交換器
JP2009103360A (ja) * 2007-10-23 2009-05-14 Tokyo Roki Co Ltd プレート積層型熱交換器
JP2010203631A (ja) * 2009-02-27 2010-09-16 Tokyo Radiator Mfg Co Ltd Ｕターンチューブ
JP2011007463A (ja) * 2009-06-29 2011-01-13 Sanden Corp 冷却装置
JP2014500469A (ja) * 2010-11-10 2014-01-09 ヴァレオ クリマジステーメ ゲーエムベーハー 車両用のプレート型熱交換器および空調回路

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KR0143540B1 (ko) * 1992-08-27 1998-08-01 코오노 미찌아끼 편평튜브와 물결형휜을 교호로 적층해서 이루어진 적층형 열교환기 및 그 제조방법
US5632331A (en) * 1993-09-30 1997-05-27 Sanden Corporation Heat exchanger

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS637723U (fr) * 1986-06-30 1988-01-19
JPH0417263U (fr) * 1990-05-25 1992-02-13
JPH06123581A (ja) * 1992-10-09 1994-05-06 Mitsubishi Heavy Ind Ltd 積層型熱交換器
JP2009103360A (ja) * 2007-10-23 2009-05-14 Tokyo Roki Co Ltd プレート積層型熱交換器
JP2010203631A (ja) * 2009-02-27 2010-09-16 Tokyo Radiator Mfg Co Ltd Ｕターンチューブ
JP2011007463A (ja) * 2009-06-29 2011-01-13 Sanden Corp 冷却装置
JP2014500469A (ja) * 2010-11-10 2014-01-09 ヴァレオ クリマジステーメ ゲーエムベーハー 車両用のプレート型熱交換器および空調回路

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CN109073337A (zh) 2018-12-21

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