WO2019216183A1 - Échangeur de chaleur de type à plaques stratifiées - Google Patents

Échangeur de chaleur de type à plaques stratifiées Download PDF

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Publication number
WO2019216183A1
WO2019216183A1 PCT/JP2019/017067 JP2019017067W WO2019216183A1 WO 2019216183 A1 WO2019216183 A1 WO 2019216183A1 JP 2019017067 W JP2019017067 W JP 2019017067W WO 2019216183 A1 WO2019216183 A1 WO 2019216183A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
plate
heat exchanger
tank space
cross
Prior art date
Application number
PCT/JP2019/017067
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English (en)
Japanese (ja)
Inventor
智史 二田
功 玉田
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 JP2019079353A external-priority patent/JP2019200039A/ja
Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Publication of WO2019216183A1 publication Critical patent/WO2019216183A1/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
    • 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
    • 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 plate stack type heat exchanger.
  • the heat exchanger described in Patent Document 1 has a structure in which a plurality of plate members are stacked and arranged with a predetermined gap therebetween. Offset fins are arranged in the gaps between adjacent plate members. A gap between adjacent plate members constitutes a coolant channel through which a coolant flows and a cooling water channel through which cooling water flows. The refrigerant channel and the cooling water channel are alternately arranged in the stacking direction of the plate members.
  • a first outermost plate member disposed on one end side in the stacking direction is provided with a first joint that constitutes a cooling water inlet and a first cooling water pipe that constitutes a cooling water outlet.
  • a second outermost plate member disposed on the other end side in the stacking direction is provided with a second joint that constitutes a refrigerant outlet and a second cooling water pipe that constitutes a cooling water inlet. ing.
  • the plurality of plate-like members include a cooling water tank space that distributes the cooling water flowing from the first joint to the plurality of cooling water flow paths, and a refrigerant for distributing the refrigerant flowing from the second joint to the plurality of refrigerant flow paths.
  • a tank space is formed.
  • the flow rate of the liquid-phase refrigerant distributed from the other intermediate portion of the refrigerant tank space to the refrigerant flow path is larger. Such a deviation in the flow rate of the liquid-phase refrigerant distributed to the plurality of refrigerant channels tends to occur particularly in a plate-stacked heat exchanger having a short length in the stacking direction.
  • the heat exchange amounts of the plurality of refrigerant flow paths and the plurality of cooling water flow paths also vary. This is not preferable because it causes a decrease in the heat exchange performance of the heat exchanger.
  • An object of the present disclosure is to provide a plate stack type heat exchanger capable of improving heat exchange performance.
  • a plate stacking type heat exchanger includes a heat exchanging unit including a plurality of plate members that are stacked and arranged with a gap therebetween, and a plurality of refrigerant flows between the plurality of plate members.
  • the first flow path and a plurality of second flow paths through which a predetermined fluid flows are formed, and heat exchange is performed between the refrigerant flowing through the first flow path and the second flow path and the predetermined fluid.
  • the heat exchange part has a tank space and a throttle part.
  • the tank space is formed so as to extend in the plate stacking direction when the direction in which the plurality of plate members are stacked and arranged is the plate stacking direction, communicates with the plurality of first flow paths, and flows from the inflow portion.
  • a refrigerant having a two-phase state of a gas phase and a liquid phase is distributed to the plurality of first flow paths.
  • the throttle part partially reduces the cross-sectional area of the tank space in the direction orthogonal to the plate stacking direction.
  • FIG. 1 is a front view showing a front structure of a plate-stacked heat exchanger according to the first embodiment.
  • FIG. 2 is a plan view showing a planar structure of the plate stack type heat exchanger according to the first embodiment.
  • FIG. 3 is an exploded view showing an exploded structure of the plate stacking type heat exchanger according to the first embodiment.
  • FIG. 4 is a cross-sectional view showing a cross-sectional structure taken along line IV-IV in FIG.
  • FIG. 5 is a cross-sectional view showing a cross-sectional structure around the aperture portion of the first embodiment.
  • FIG. 6 is a cross-sectional view showing a cross-sectional structure of a plate stacking type heat exchanger according to a first modification of the first embodiment.
  • FIG. 1 is a front view showing a front structure of a plate-stacked heat exchanger according to the first embodiment.
  • FIG. 2 is a plan view showing a planar structure of the plate stack type heat exchanger according to the first embodiment.
  • FIG. 7 is a cross-sectional view showing a cross-sectional structure of a plate-stacked heat exchanger according to a first modification of the first embodiment.
  • FIG. 8 is a cross-sectional view showing a cross-sectional structure of a plate stack type heat exchanger according to a second modification of the first embodiment.
  • FIG. 9 is a graph showing the relationship between the number of stages of cooling water flow paths and the cooling ratio in a plate-stacked heat exchanger not provided with a throttle.
  • FIG. 10 is a graph showing the relationship between the number of stages of the cooling water flow path and the cooling ratio in the plate stack type heat exchanger of the second embodiment.
  • FIG. 11 is a cross-sectional view showing a cross-sectional structure of a plate-stacked heat exchanger according to another embodiment.
  • a heat exchanger 10 shown in FIG. 1 cools cooling water by exchanging heat between, for example, cooling water for cooling a storage battery mounted on a vehicle and a refrigerant having a temperature lower than that of the cooling water. Used as equipment.
  • the cooling water corresponds to a predetermined fluid having a temperature higher than that of the refrigerant.
  • the heat exchanger 10 includes a heat exchange unit HU in which a plurality of plate members 20 are stacked in the Z-axis direction. That is, in the present embodiment, the Z-axis direction corresponds to the plate stacking direction.
  • Z1 direction one direction of the Z-axis direction
  • Z2 direction the opposite direction
  • each plate member 20 as indicated by the one-dot chain line and the two-dot chain line, a refrigerant flow path W1 through which the refrigerant flows and a cooling water flow path W2 through which the cooling water flows are formed.
  • coolant flow path W1 and the some cooling water flow path W2 are arrange
  • the refrigerant flow path W1 corresponds to the first flow path
  • the cooling water flow path W2 corresponds to the second flow path.
  • the heat exchanger 10 has a substantially rectangular cross-sectional shape perpendicular to the Z-axis direction.
  • the longitudinal direction and the short direction of the heat exchanger 10 are referred to as “X-axis direction” and “Y-axis direction”, respectively.
  • One direction of the X-axis direction is referred to as “X1 direction”, and the opposite direction is referred to as “X2 direction”.
  • a first refrigerant tank space T11 and a second refrigerant tank space T12 are formed inside the two corners of the four corners of the heat exchanger 10 so as to extend in the Z-axis direction. Yes.
  • a first cooling water tank space T21 and a second cooling water tank space T22 are formed in the remaining two corners located on the diagonal line so as to extend in the Z-axis direction.
  • a refrigerant inflow portion 82 communicated with the first refrigerant tank space T11 and a cooling water outflow portion 83 communicated with the first cooling water tank space T21. Is provided.
  • a refrigerant outflow part 80 communicated with the second refrigerant tank space T12 and a second cooling water tank space T22 communicated.
  • the cooling water inflow portion 81 is provided.
  • a refrigerant having a two-phase state of a gas phase and a liquid phase flows in from the refrigerant inflow portion 82, and cooling water flows in from the cooling water inflow portion 81.
  • the refrigerant that has flowed into the first refrigerant tank space T ⁇ b> 11 from the refrigerant inflow portion 82 is distributed to a plurality of refrigerant flow paths W ⁇ b> 1 inside the heat exchanger 10.
  • the refrigerant that has flowed through the plurality of refrigerant flow paths W1 is collected in the second refrigerant tank space T12 and then flows out of the refrigerant outflow portion 80.
  • the cooling water that has flowed into the second cooling water tank space T22 from the cooling water inflow portion 81 is distributed to the plurality of cooling water flow paths W2 inside the heat exchanger 10.
  • the cooling water that has flowed through the plurality of cooling water flow paths W2 is collected in the first cooling water tank space T21 and then flows out from the cooling water outflow portion 83.
  • the cooling water is cooled by heat exchange between the refrigerant flowing through the refrigerant flow path W1 and the cooling water flowing through the cooling water flow path W2.
  • the heat exchanger 10 includes a plate member 20, a refrigerant fin 30, a cooling water fin 40, a first outermost shell plate 50, and a second outermost shell plate 60.
  • a plate member 20 a refrigerant fin 30, a cooling water fin 40, a first outermost shell plate 50, and a second outermost shell plate 60.
  • These members are made of a metal material such as aluminum.
  • the plate member 20 includes an outer plate 21 and an inner plate 22.
  • the outer plate 21 is made of a plate-like member having a cross-sectional shape orthogonal to the Z-axis direction formed in a substantially rectangular shape.
  • the plurality of outer plates 21 are arranged so that the tip portions of the respective overhanging portions 210 face the Z1 direction, and are stacked as shown in FIG.
  • the overhang portions 210 of the plurality of outer plates 21 are joined to each other by brazing.
  • a protrusion 212 that protrudes in a cylindrical shape in the Z2 direction is formed at a position corresponding to the first refrigerant tank space T11 in the outer plate 21 with an axis m1 parallel to the Z-axis direction as a center. ing.
  • the internal space of the protrusion 212 is a through hole 211 that penetrates the outer plate 21 in the Z-axis direction along the axis m1.
  • the inner plate 22 is made of a plate-like member having a cross-sectional shape orthogonal to the Z-axis direction formed in a substantially rectangular shape. As shown in FIG. 3, the inner plate 22 is disposed in a gap between the outer plates 21 and 21 adjacent in the Z-axis direction. The inner plate 22 is joined to the outer plates 21 and 21 adjacent in the Z-axis direction by brazing. As shown in FIG. 4, the inner plate 22 divides a space formed between adjacent outer plates 21 and 21 into independent refrigerant flow paths W1 and cooling water flow paths W2 that are not communicated with each other. Yes.
  • the inner plate 22 is formed with a protruding portion 221 that protrudes in a cylindrical shape in the Z1 direction about the axis m1 at a portion corresponding to the through hole 211 of the outer plate 21.
  • the protrusion 221 is formed with a burring hole 220 that penetrates the outer plate 21 in the Z-axis direction along the axis m1.
  • the burring hole 220 is formed when burring the first refrigerant tank space T11 in the heat exchanger 10.
  • the outer peripheral surface of the protrusion 221 is joined to the inner peripheral surface of the through hole 211 of the outer plate 21 by brazing.
  • the first refrigerant tank space T11 is configured by connecting the through holes 211 of the plurality of inner plates 22 in the Z-axis direction by such a joining structure. That is, the first refrigerant tank space T11 is formed so as to extend along the axis m1. In the heat exchanger 10 of the present embodiment, the length L of the first refrigerant tank space T11 is set to 110 mm or less.
  • the first refrigerant tank space T11 is communicated with a plurality of refrigerant flow paths W1 through an inlet P formed between the inner plate 22 and the outer plate 21.
  • the first refrigerant tank space T11 and the cooling water flow path W2 are partitioned by the joint structure of the protrusion 212 of the outer plate 21 and the protrusion 221 of the inner plate 22, so that the first refrigerant tank space T11 and the cooling water flow path W2 Communication is blocked. That is, the first refrigerant tank space T11 communicates only with the plurality of refrigerant flow paths W1.
  • the first refrigerant tank orthogonal to the Z-axis direction is provided at the protrusion 221 disposed at a position shifted in the Z2 direction from the intermediate position in the Z-axis direction.
  • the narrowed portion 222 is formed so as to partially narrow the cross-sectional area of the space T11.
  • the portion corresponding to the tip of the protruding portion 221 is the narrowest. That is, the minimum value of the cross-sectional area of the burring hole 220 orthogonal to the Z-axis direction is “S1” shown in FIG.
  • This cross-sectional area S1 corresponds to the minimum value of the cross-sectional area of the first refrigerant tank space T11 in the portion excluding the throttle portion 222.
  • the cross-sectional area S2 of the flow hole 222a of the throttle part 222 orthogonal to the Z-axis direction is smaller than the minimum value S1 of the cross-sectional area of the first refrigerant tank space T11.
  • the throttle part 222 is not formed in the second refrigerant tank space T12, the first cooling water tank space T21, and the second cooling water tank space T22.
  • the second refrigerant tank space T12, the first cooling water tank space T21, and the second cooling water tank space T22 have a similar structure to the first refrigerant tank space T11 except that the throttle portion 222 is not formed. Therefore, a detailed description of their structure is omitted.
  • the refrigerant fins 30 are respectively disposed in a plurality of refrigerant flow paths W ⁇ b> 1 formed between the outer plate 21 and the inner plate 22.
  • the cooling water fins 40 are respectively disposed in a plurality of cooling water flow paths W ⁇ b> 2 formed between the outer plate 21 and the inner plate 22.
  • the refrigerant fin 30 and the cooling water fin 40 for example, corrugated fins formed in a wave shape can be used.
  • the refrigerant fin 30 and the cooling water fin 40 have a function of improving the heat exchange performance of the heat exchanger 10 by increasing the heat transfer area.
  • the first outermost shell plate 50 is fixed to the inner plate 22 disposed at the extreme end in the Z1 direction by brazing.
  • the first outermost shell plate 50 is provided with a refrigerant inflow portion 82 and a cooling water outflow portion 83.
  • the first outermost shell plate 50 closes one end of the second refrigerant tank space T12 in the Z1 direction and one end of the second coolant tank space T22 in the Z1 direction.
  • the cross-sectional area S3 of the refrigerant inflow portion 82 orthogonal to the Z-axis direction is smaller than the minimum value S1 of the cross-sectional area of the first refrigerant tank space T11.
  • the second outermost shell plate 60 is fixed to the outer plate 21 disposed at the endmost portion in the Z2 direction by brazing.
  • the second outermost shell plate 60 is assembled with the refrigerant outflow portion 80 and the cooling water inflow portion 81 shown in FIG.
  • the second outermost shell plate 60 closes one end portion in the Z2 direction of the first refrigerant tank space T11 and one end portion in the Z1 direction of the first cooling water tank space T21.
  • liquid phase refrigerant flows in into refrigerant channel W1 through a plurality of inflow parts P1 arranged in the Z1 direction side rather than throttling part 222 among a plurality of inflow ports P arranged near throttle part 222. Therefore, it is possible to increase the flow rate of the liquid-phase refrigerant flowing from the inflow portion P1 into the refrigerant flow path W1.
  • a part of the liquid-phase refrigerant that has become a jet flows through the flow hole 222 a of the throttle portion 222.
  • the liquid phase refrigerant flows so as to be folded back in the Z1 direction by reaching the end of the first refrigerant tank space T11 in the Z2 direction due to inertia and colliding with the second outermost shell plate 60.
  • the liquid-phase refrigerant that has flowed so as to be folded back reaches the throttle portion 222 and is blocked.
  • liquid phase refrigerant flows into refrigerant channel W1 through a plurality of inflow parts P2 arranged in the Z2 direction side rather than throttling part 222 among a plurality of inflow ports P arranged near the restricting part 222. Therefore, it is possible to increase the flow rate of the liquid phase refrigerant flowing from the inflow portion P2 into the refrigerant flow path W1.
  • the operations and effects shown in the following (1) to (7) can be obtained.
  • the length L of the first refrigerant tank space T11 in the Z-axis direction is set to 110 mm or less.
  • a part of the liquid-phase refrigerant that has flowed into the first refrigerant tank space T11 from the refrigerant inflow portion 82 easily collides with the second outermost shell plate 60.
  • the flow rate variations in the plurality of refrigerant flow paths W1 are likely to occur. Therefore, it is effective to adopt the structure of the heat exchanger 10 of this embodiment.
  • the flow direction of the refrigerant flowing into the first refrigerant tank space T11 from the refrigerant inflow portion 82 is parallel to the axis m1, that is, parallel to the extending direction of the first refrigerant tank space T11.
  • a part of the liquid-phase refrigerant that has flowed into the first refrigerant tank space T11 from the refrigerant inflow portion 82 easily collides with the second outermost shell plate 60.
  • the flow rate variations in the plurality of refrigerant flow paths W1 are likely to occur. Therefore, it is effective to adopt the structure of the heat exchanger 10 of this embodiment.
  • the cross-sectional area S2 of the throttle part 222 orthogonal to the Z-axis direction is based on the minimum value S1 of the cross-sectional area of the portion excluding the throttle part 222 in the cross-sectional area of the first refrigerant tank space T11 orthogonal to the Z-axis direction. Is also small.
  • a part of the liquid-phase refrigerant that has flowed into the first refrigerant tank space T11 from the refrigerant inflow portion 82 collides with the throttle portion 222 more reliably.
  • the liquid refrigerant flowing so as to be folded back in the Z1 direction by colliding with the second outermost shell plate 60 also collides with the throttle portion 222 more reliably.
  • the flow rate of the liquid phase refrigerant flowing into the refrigerant flow path W1 located near the middle of the first refrigerant tank space T11 can be increased more reliably, the liquid phase refrigerant distributed to the plurality of refrigerant flow paths W1. It is possible to more accurately suppress the deviation of the flow rate distribution.
  • the first refrigerant tank space T11 and the refrigerant inflow portion 82 are disposed on the same axis m1, and have a cross-sectional shape of the first refrigerant tank space T11 orthogonal to the Z-axis direction.
  • the position of the center of gravity coincides with the position of the center of gravity of the cross-sectional shape of the refrigerant inflow portion 82 orthogonal to the Z-axis direction.
  • a part of the liquid-phase refrigerant that has flowed into the first refrigerant tank space T11 from the refrigerant inflow portion 82 easily collides with the second outermost shell plate 60.
  • the flow rate variations in the plurality of refrigerant flow paths W1 are likely to occur. Therefore, it is effective to adopt the structure of the heat exchanger 10 of this embodiment.
  • the cross-sectional area of the flow holes 222a of the throttle parts 222 may be changed. Thereby, for example, it is possible to balance the flow rate of the refrigerant flowing in the Z2 direction through the flow hole 222a of the throttle unit 222 and the flow rate of the refrigerant flowing in the Z1 direction by colliding with the throttle unit 222. It is.
  • throttle portions 222 (1) to 222 (3) are provided in the first refrigerant tank space T11 in order from the vicinity of the refrigerant inflow portion 82.
  • the cross-sectional areas S21 to S23 of the flow holes 222a of the narrowed portions 222 (1) to 222 (3) have a relationship of “S21> S22> S23”.
  • most of the refrigerant that flows into the first refrigerant tank space T11 from the refrigerant inflow portion 82 and reaches the throttle portion 222 (1) does not collide with the throttle portion 222 (1). It flows downstream through the flow hole 222a.
  • coolant can be appropriately distributed to the refrigerant
  • the refrigerant may flow from the refrigerant inflow portion 82 into the first refrigerant tank space T11 in the form of a jet.
  • the cross-sectional areas S21 to S23 of the flow holes 222a of the throttle portions 222 (1) to 222 (3) are in a relationship of “S21 ⁇ S22 ⁇ S23” according to the spread of the jet of refrigerant. You may set as follows.
  • the cross-sectional areas S21 to S23 of the flow holes 222a of the throttle portions 222 (1) to 222 (3) are appropriately changed in accordance with the structure of the heat exchanger 10, the refrigerant flow in each refrigerant flow path W1 is changed. Since the distribution can be improved, as a result, the heat exchange performance of the heat exchanger 10 can be improved.
  • a first refrigerant tank space T11 is configured by through holes 214 and 224 formed so as to penetrate the mating surface 213a of the outer plate 21 and the mating surface 223a of the inner plate 22, respectively.
  • At least one inner plate 22 is formed with a throttle portion 225 so as to partially narrow the cross-sectional area of the first refrigerant tank space T11 orthogonal to the Z-axis direction.
  • the portion corresponding to the tip portions of the protruding portions 213 and 223 of the plates 21 and 22 is the narrowest in the portion excluding the throttle portion 225. It has become. That is, of the cross-sectional area of the first refrigerant tank space T11 orthogonal to the Z direction, the minimum value of the cross-sectional area of the portion excluding the throttle portion 225 is “S1” shown in FIG.
  • the cross-sectional area S2 of the hole 225a of the throttle portion 225 orthogonal to the Z-axis direction is smaller than the minimum value S1 of the cross-sectional area of the first refrigerant tank space T11.
  • the expansion part 225 may be formed in the protrusion part 213 of the outer plate 21.
  • the narrowed portion 225 may be formed on both the protruding portion 213 of the outer plate 21 and the protruding portion 223 of the inner plate 22.
  • the inventors of the present invention have a conventional heat exchanger that is not provided with a throttle portion, and the flow rate of the refrigerant flowing through the refrigerant flow path disposed near the central portion of the refrigerant tank space is likely to be smaller than other portions. Have been confirmed through experiments and simulations. From the results of experiments, simulations, and the like, it is preferable to arrange the throttle portion near the center of the refrigerant tank space in consideration of the refrigerant distribution in each refrigerant flow path. Hereinafter, a preferable arrangement of the throttle part will be described in detail.
  • the inventors have provided between the adjacent refrigerant flow paths W1 and W1 when the refrigerant is introduced from the refrigerant inflow part 82.
  • the cooling degree of the cooling water flowing through the cooling water flow path is measured.
  • the measurement results are as shown in the bar graph shown in FIG.
  • the horizontal axis of the bar graph indicates the number of stages of the cooling water flow paths sequentially attached from the cooling water flow path closest to the refrigerant inflow portion 82. Specifically, numbers from “1” to “14” are assigned as the number of steps in order from the cooling water flow path closest to the refrigerant inflow portion 82.
  • the vertical axis of the bar graph indicates the ratio of the cooling degree in each cooling water flow channel to the average value when the average cooling water cooling value in each cooling water flow channel is “1”. For example, a cooling water passage having a cooling ratio exceeding “1” means that the cooling water passage is easier to cool than the average. Conversely, a cooling water channel having a cooling ratio of less than “1” means that the cooling water channel is more difficult to cool than average.
  • the cooling ratio of the cooling water flow paths having the number of stages “6” to “13” is less than “1”.
  • the cooling water flow path having a cooling ratio of less than “1” it is assumed that the cooling water is more difficult to cool than the average because the flow rate of the refrigerant flowing through the adjacent refrigerant flow path W1 is small.
  • the flow rate of the refrigerant flowing through the refrigerant flow paths W1d and W1e adjacent thereto is small.
  • the flow rate of the refrigerant in the refrigerant flow path can be increased, it is possible to efficiently improve the refrigerant distribution in the heat exchanger 10.
  • increasing the refrigerant flow rate in the refrigerant flow paths W1a to W1g corresponding to the cooling water flow paths having the number of stages “6” to “13” is effective in improving the refrigerant distribution.
  • FIG. 10 shows, as an example, the cooling ratio of each cooling water flow path when the throttle portion 222 is provided at a position corresponding to the cooling water flow path having the number of stages “10”.
  • the throttle portion 222 when the throttle portion 222 is provided, not only the flow rate of the refrigerant in the refrigerant channels W1d and W1e adjacent to the cooling water channel having the number of stages “10”, but also other refrigerant channels W1a It has been confirmed that the flow rates of the refrigerants W1c, W1f, and W1g also increase.
  • the inventors set the length of the refrigerant tank space T11 in the plate stacking direction Z to “L” and the refrigerant tank in the plate stacking direction Z as shown in FIG.
  • the position of the space T11 from the refrigerant inflow portion 82 is “x”
  • the distribution of the refrigerant in the heat exchanger 10 can be improved by forming the throttle portion 222 at a position that satisfies the following expression f1. And has gained knowledge.
  • the operation and effect shown in the following (8) can be obtained.
  • the heat exchanger 10 is provided with the throttle 222 so as to satisfy the above formula f1. According to such a configuration, the refrigerant distribution in each refrigerant flow path W1 can be improved, and as a result, the heat exchange performance of the heat exchanger 10 can be further improved.
  • the throttle unit 222 may be configured by a component separate from the plate member 20.
  • the narrowed portion 222 may be formed on a member 23 separate from the plate member 20, and the member 23 may be joined to the inner surface of the burring hole 220 by brazing or the like.
  • the refrigerant outflow part 80, the cooling water inflow part 81, the refrigerant inflow part 82, and the cooling water outflow part 83 may all be provided on the upper surface of the heat exchanger 10. Alternatively, all of the refrigerant outflow portion 80, the cooling water inflow portion 81, the refrigerant inflow portion 82, and the cooling water outflow portion 83 may be provided on the bottom surface of the heat exchanger 10.
  • the two types of fluids used for heat exchange in the heat exchanger 10 are not limited to cooling water for cooling the storage battery and refrigerant for cooling the cooling water, but may be any one of hot water and low-temperature refrigerant, etc. Two types of fluids can be used.
  • the heat exchanger 10 of each embodiment can be used for arbitrary heat exchange systems.
  • the heat exchanger 10 of each embodiment is a heat exchange system that cools cooling water for cooling a battery, a motor generator, an inverter, a substrate, and the like using a refrigerant having a temperature lower than that of the cooling water in the heat pump system. It can be used as a container.
  • the heat pump system in which the heat exchanger is used may be a system that uses the exhaust heat of the battery or the like recovered by the heat exchanger for heating the interior of the vehicle through a water-cooled condenser or a heater core. It may be a system that radiates heat to the outside air.

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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 de chaleur (10) comprenant une unité d'échange de chaleur (HU) constituée d'une pluralité d'éléments plaque stratifiés (20). L'échangeur de chaleur a un espace de réservoir (T11) et une partie d'étranglement (222). L'espace de réservoir est formé de façon à s'étendre dans la direction de stratification de plaques, est en communication avec une pluralité de premiers trajets d'écoulement (W1) et distribue, à la pluralité de premiers trajets d'écoulement, un fluide frigorigène s'écoulant à partir d'une section d'entrée (82) et présentant un état diphasique constitué d'une phase gazeuse et d'une phase liquide. La partie d'étranglement réduit partiellement la surface de section transversale de l'espace de réservoir dans une direction orthogonale à la direction de stratification de plaques.
PCT/JP2019/017067 2018-05-11 2019-04-22 Échangeur de chaleur de type à plaques stratifiées WO2019216183A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2018-092480 2018-05-11
JP2018092480 2018-05-11
JP2019079353A JP2019200039A (ja) 2018-05-11 2019-04-18 プレート積層型の熱交換器
JP2019-079353 2019-04-18

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WO2019216183A1 true WO2019216183A1 (fr) 2019-11-14

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Citations (5)

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Publication number Priority date Publication date Assignee Title
JP2001221589A (ja) * 2000-01-08 2001-08-17 Halla Aircon Co Ltd 熱交換性能を向上させた積層型熱交換器用プレート及びこれを用いる熱交換器
JP2001221535A (ja) * 2000-02-08 2001-08-17 Denso Corp 冷媒蒸発器
US20090074627A1 (en) * 2003-10-27 2009-03-19 Velocys Inc. Manifold designs, and flow control in mulitchannel microchannel devices
WO2012176336A1 (fr) * 2011-06-24 2012-12-27 三菱電機株式会社 Élément chauffant à plaques et dispositif de cycle de réfrigération
US20180100706A1 (en) * 2016-10-11 2018-04-12 Climate Master, Inc. Enhanced heat exchanger

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