WO2018131596A1 - Échangeur thermique à eau - Google Patents

Échangeur thermique à eau Download PDF

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Publication number
WO2018131596A1
WO2018131596A1 PCT/JP2018/000309 JP2018000309W WO2018131596A1 WO 2018131596 A1 WO2018131596 A1 WO 2018131596A1 JP 2018000309 W JP2018000309 W JP 2018000309W WO 2018131596 A1 WO2018131596 A1 WO 2018131596A1
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WO
WIPO (PCT)
Prior art keywords
flow path
fluid
heat exchanger
layer
water heat
Prior art date
Application number
PCT/JP2018/000309
Other languages
English (en)
Japanese (ja)
Inventor
柴田　豊
Original Assignee
ダイキン工業株式会社
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 ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Priority to EP18738883.0A priority Critical patent/EP3569962B1/fr
Priority to US16/477,705 priority patent/US20190360758A1/en
Priority to CN201880006479.6A priority patent/CN110168300B/zh
Publication of WO2018131596A1 publication Critical patent/WO2018131596A1/fr

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    • 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
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/048—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of ribs integral with the element or local variations in thickness of the element, e.g. grooves, microchannels
    • 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
    • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • 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
    • 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
    • F28D9/0031—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 conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—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 conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—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 conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • 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
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element

Definitions

  • the present invention relates to a water heat exchanger, in particular, a first layer in which a plurality of first flow paths through which water as a first fluid flows is formed, and a plurality of second flow paths through which refrigerant as a second fluid flows. It is related with the water heat exchanger which is comprised by laminating
  • a water heat exchanger that performs heat exchange between water as a first fluid and a refrigerant (such as a chlorofluorocarbon refrigerant, a natural refrigerant, or a brine) as a second fluid has been provided. in use.
  • a refrigerant such as a chlorofluorocarbon refrigerant, a natural refrigerant, or a brine
  • Patent Document 1 Japanese Patent Laid-Open No. 2010-117102
  • a first layer in which a plurality of first flow paths through which a first fluid flows is formed
  • a second fluid There is a configuration in which a second layer in which a plurality of second flow paths are formed is stacked.
  • An object of the present invention is to provide a first layer in which a plurality of first flow paths through which water as a first fluid flows is formed, and a second layer in which a plurality of second flow paths through which a refrigerant as a second fluid flows are formed.
  • a hydrothermal exchanger that exchanges heat between the first fluid and the second fluid, the high-performance and compact design is achieved by devising the shape of the flow path. is there.
  • the water heat exchanger includes a first layer in which a plurality of first flow paths through which water as a first fluid flows is formed, and a plurality of second flow paths through which refrigerant as a second fluid flows.
  • the formed second layer is laminated to perform heat exchange between the first fluid and the second fluid.
  • the first flow path has one end from the other end along the direction intersecting the arrangement direction of the first flow paths when the first layer is viewed along the stacking direction of the first and second layers. It extends to the part.
  • the second flow path extends from one end of the second layer to the other end along the direction intersecting the arrangement direction of the second flow paths when the second layer is viewed along the stacking direction.
  • the first flow path has a meandering shape when the first layer is viewed along the stacking direction, and / or the second flow path is first along the stacking direction. When the two layers are viewed, it has a meandering shape.
  • the first flow path and the second flow path have a meandering shape when the first layer and the second layer are viewed along the stacking direction.
  • the flow path length per unit volume of the water heat exchanger can be increased.
  • the heat-transfer promotion effect can be acquired by the meandering shape of such a 1st flow path and a 2nd flow path, compared with the case where the 1st flow path and the 2nd flow path have a straight shape.
  • the heat transfer coefficient in the first flow path and the second flow path can be improved.
  • the performance and compactness of the water heat exchanger can be achieved here.
  • the water heat exchanger according to the second aspect is the water heat exchanger according to the first aspect.
  • the first flow path is in the vicinity of the outlet of the first fluid.
  • the channel cross-sectional area in the vicinity of the first fluid outlet located is formed so as to be larger than the channel cross-sectional area in the portion upstream of the first fluid outlet vicinity.
  • the flow passage cross-sectional area in the vicinity of the first fluid outlet is larger than the upstream portion of the first flow passage, the flow velocity of the first fluid in the first flow passage is reduced. It is possible to prevent the scale that deposits when the first fluid is heated from clogging in the vicinity of the first fluid outlet, while limiting the decrease in the heat transfer coefficient due to the above. Thus, the clogging of the first flow path in the water heat exchanger can be suppressed while minimizing the decrease in the heat transfer coefficient.
  • the second flow path is formed of the second fluid.
  • the channel cross-sectional area in the vicinity of the second fluid outlet located in the vicinity of the outlet is formed to be larger than the channel cross-sectional area in the upstream portion of the vicinity of the second fluid outlet.
  • the flow passage cross-sectional area in the vicinity of the second fluid outlet is larger than the upstream portion of the second flow passage, the flow velocity of the second fluid in the second flow passage is reduced.
  • the second fluid containing a large amount of gas components that increase with evaporation can be smoothly flowed to the vicinity of the second fluid outlet, while the decrease in the heat transfer coefficient due to the above is limited only to the vicinity of the second fluid outlet.
  • FIG. 2 It is a figure (corresponding to Drawing 2) showing the 1st channel of the water heat exchanger concerning modification 5 of the present invention. It is a figure (corresponding to Drawing 2) showing the 1st channel of the water heat exchanger concerning modification 5 of the present invention. It is a figure (corresponding to Drawing 3) showing the 2nd channel of the water heat exchanger concerning modification 6 of the present invention. It is a figure (corresponding to Drawing 3) showing the 2nd channel of the water heat exchanger concerning modification 6 of the present invention. It is a figure (corresponding to Drawing 3) showing the 2nd channel of the water heat exchanger concerning modification 6 of the present invention. It is a figure (corresponding to Drawing 3) showing the 2nd channel of the water heat exchanger concerning modification 6 of the present invention. It is a figure (corresponding to Drawing 3) showing the 2nd channel of the water heat exchanger concerning modification 6 of the present invention.
  • FIGS. 1 to 4 are views showing a water heat exchanger 1 according to an embodiment of the present invention.
  • the water heat exchanger 1 is a heat exchanger that performs heat exchange between water as a first fluid and refrigerant as a second fluid in a heat pump type air conditioner, a heat pump type hot water heater, or the like.
  • a heat pump type air conditioner a heat pump type hot water heater
  • these expressions are expressions for convenience of explanation, and do not mean the actual arrangement of the water heat exchanger 1 and its constituent parts.
  • the water heat exchanger 1 mainly includes a casing 2 provided with a heat exchanging unit 3 that performs heat exchange between the first fluid and the second fluid, first inlet / outlet pipes 4a and 4b that serve as inlets / outlets of the first fluid, Second inlet / outlet pipes 5a and 5b serving as inlets and outlets for the second fluid are provided.
  • the heat exchange unit 3 includes a first layer 10 in which a plurality of first flow paths 11 through which a first fluid flows are formed, a second layer 20 in which a plurality of second flow paths 21 through which a second fluid flows are formed, Are laminated.
  • the direction in which the first layer 10 and the second layer 20 are stacked (here, the direction from the front side to the back side in FIGS. 1 to 3) is defined as the stacking direction.
  • the direction in which the plurality of first flow paths 11 are arranged (here, the left-right direction in FIG. 2) is the arrangement direction of the first flow paths 11, and the direction in which the plurality of second flow paths 21 are arranged (here, FIG. 3).
  • the vertical direction of the paper surface is the arrangement direction of the second flow paths 21.
  • the direction (here, it intersects with the arrangement direction of the 1st flow path 11) 2 extends from one end of the first layer 10 (upper end of the first layer 10 in FIG. 2) to the other end (lower end of the first layer 10 in FIG. 2) along the vertical direction and vertical direction of FIG. ing.
  • the second flow path 21 is a direction that intersects with the arrangement direction of the second flow paths 21 when the second layer 20 is viewed along the stacking direction of the first and second layers 10 and 20 (here, 3 extends from one end of the second layer 20 (the left end of the second layer 20 in FIG. 3) to the other end (the right end of the second layer 20 in FIG. 3) along the horizontal direction in FIG. ing.
  • the 1st flow path 11 and the 2nd flow path 20 are arrange
  • the first flow path 11 has a meandering shape when the first layer 10 is viewed along the stacking direction.
  • the first flow path 11 is meandering linearly (that is, squared) in the arrangement direction of the first flow paths 11 (here, the left and right direction in FIG. 2). It extends in a direction (here, the vertical direction) intersecting the arrangement direction. It is preferable that the first flow path 11 meanders three or more times from one end of the first layer 10 to the other end.
  • the second flow path 21 has a meandering shape when the second layer 20 is viewed along the stacking direction.
  • the second flow path 21 is meandering linearly (that is, squarely) in the arrangement direction of the second flow paths 21 (here, the vertical direction in FIG. 3), while the second flow path 21 It extends in a direction intersecting the arrangement direction (here, the horizontal direction). It is preferable that the second flow path 21 meanders three or more times from one end of the second layer 20 to the other end.
  • the heat exchanging unit 3 having the laminated structure of the first layer 10 and the second layer 20 includes the first plate member 12 in which the groove forming the first flow path 11 is formed on one side, and the second flow path 21. And the second plate material 22 having grooves formed on one side thereof are alternately laminated.
  • plate materials 12 and 22 are formed with the metal raw material.
  • the grooves forming the first flow path 11 and the second flow path 21 are formed, for example, by subjecting the first and second plate members 12 and 22 to machining or etching.
  • the first inlet / outlet pipes 4a and 4b are provided at the upper part and the lower part of the casing 2, respectively.
  • a first header portion 6 in which a space for joining the upper end portions of the first flow path 11 is formed in the upper portion and a space for joining the lower end portions of the first flow passage 11 are formed in the lower portion thereof.
  • the first header portion 7 is provided.
  • the first inlet / outlet pipe 4 a communicates with the upper end of the first flow path 11 via the first header section 6, and the first inlet / outlet pipe 4 b passes through the first header section 7 to the first flow path. 11 communicates with the lower end portion.
  • tube 5a, 5b is provided in the left part and the right part of the casing 2 here.
  • a second header portion 8 in which a space for joining the left end portions of the second flow path 21 is formed at the left portion thereof, and a space for joining the right end portions of the second flow passage 21 at the right portion thereof.
  • a second header portion 9 formed with a.
  • the second inlet / outlet pipe 5 a communicates with the left end of the second flow path 21 via the second header portion 8, and the second inlet / outlet pipe 5 b passes through the second header section 9 to the second flow path. 21 communicates with the right end portion.
  • the first inlet / outlet pipe 4b serves as the inlet of the first fluid
  • the first inlet / outlet pipe 4a serves as the first fluid
  • the second inlet / outlet pipe 5b can be used as the inlet of the second fluid
  • the second inlet / outlet pipe 5a can be used as the outlet of the second fluid.
  • the first fluid flows through the first flow path 11 from the bottom to the top and is heated
  • the second fluid moves through the second flow path 21 from the right to the left. It will function as a heat exchanger that flows and cools.
  • the first inlet / outlet pipe 4b is used as the inlet of the first fluid
  • the first inlet / outlet pipe 4a is used as the outlet of the first fluid
  • the second inlet / outlet pipe 5a can be used as an inlet for the second fluid
  • the second inlet / outlet pipe 5b can be used as an outlet for the second fluid.
  • the first fluid flows in the first flow path 11 from the bottom to the top and is cooled
  • the second fluid moves in the second flow path 21 from the left to the right. It functions as a heat exchanger that flows and heats.
  • the first flow path 11 and the second flow path 21 have a meandering shape when the first layer 10 and the second layer 20 are viewed along the stacking direction. Therefore, compared with the case where the 1st flow path 11 and the 2nd flow path 21 have a straight shape, the flow path length per unit volume of the water heat exchanger 1 can be enlarged. In addition, since the heat transfer promoting effect can be obtained by the meandering shape of the first flow path 11 and the second flow path 21, the first flow path 11 and the second flow path 21 have a straight shape. Compared with the case where it exists, the heat transfer rate in the 1st flow path 11 and the 2nd flow path 21 can be improved. Thus, the high performance and compactness of the water heat exchanger 1 can be achieved here.
  • the first and second flow paths 11 and 21 may have a curved shape (that is, rounded without being squared).
  • both the first and second flow paths 11 and 21 have a meandering shape, but only the first flow path 11 or the second flow path 21 is provided. May have a meandering shape.
  • the second flow path 21 may have a meandering shape as shown in FIGS. 3 and 6, and the first flow path 11 may have a straight shape as shown in FIG.
  • the first flow path 11 has a meandering shape as shown in FIGS. 2 and 5
  • the second flow path 21 has a straight shape as shown in FIG. Also good.
  • the second flow path that extends from one end of the second layer 20 (the left end of the second layer 20 in FIG. 3) to the other end (the right end of the second layer 20 in FIG. 3) along the horizontal direction. 9 and 10, as shown in FIGS. 9 and 10, from one end of the second layer 20 (the lower end of the second layer 20 in FIG. 10) to the other end (the upper end of the second layer 20 in FIG. 10) along the vertical direction.
  • the first flow path 11 and the second flow path 21 may be arranged so as to form a counter flow (or parallel flow).
  • the second inlet / outlet pipes 5 a and 5 b and the second headers 8 and 9 are provided at the lower part and the upper part of the casing 2.
  • the first fluid when the first fluid is heated by the second fluid, the first fluid flows through the first flow path 11 from the bottom to the top and is heated, and the second fluid flows through the second flow path 21 from the top. It will function as a heat exchanger that flows downward and is cooled.
  • the first fluid when the first fluid is cooled by the second fluid, the first fluid flows through the first flow path 11 from the bottom to the top and is cooled, and the second fluid flows through the second flow path 21. It will function as a heat exchanger that flows from bottom to top and is heated.
  • the second channel 21 is divided into a plurality of channel groups, and these channel groups are connected in series so that the first channel 11 and the second channel 21 are orthogonally opposed ( Alternatively, they may be arranged so as to form an orthogonal parallel flow.
  • the second flow path 21 is divided into three flow path groups 21A, 21B, and 21C in the arrangement direction of the second flow paths 21 (here, the vertical direction in FIG. 11). is doing.
  • the flow path groups 21A, 21B, and 21C of the second flow path 21 are connected in series via the second headers 8 and 9, and the first flow path 11 and the second flow path 21 are orthogonally opposed ( (Or orthogonal parallel flow).
  • the first fluid when the first fluid is heated by the second fluid, the first fluid flows through the first flow path 11 from the bottom to the top and is heated, and the second fluid flows through the second flow path 21.
  • It will function as a heat exchanger that flows from top to bottom while being folded back to the left and right in the order of the groups 21A, 21B, and 21C and that is cooled.
  • the first fluid when the first fluid is cooled by the second fluid, the first fluid flows through the first flow path 11 from the bottom to the top and is cooled, and the second fluid flows through the second flow path 21.
  • It will function as a heat exchanger that flows and heats from the bottom to the top while being folded left and right in the order of the flow path groups 21C, 21B, and 21A.
  • connection channels 29a and 29b having the same functions as the spaces 8b and 9b may be formed at the left end and the right end of the second channel 21. That is, the connection flow path 29a that communicates between the left ends of the second flow paths 21 constituting the flow path groups 21A and 21B and the right end of the second flow path 21 that constitutes the flow path groups 21B and 21C are communicated.
  • the connection flow path 29b to be formed is formed in the second layer 20.
  • plate material 22 can be formed.
  • the second header 8 can have only a space corresponding to the space 8a in FIG. 11, and the second header 9 can have only a space corresponding to the space 9a in FIG.
  • the flow passage cross-sectional area S11a in the first fluid outlet vicinity portion 11a located in the first fluid outlet is formed so as to be larger than the flow passage cross-sectional area S11b in the portion 11b upstream of the first fluid outlet vicinity portion 11a.
  • the flow path width W11a of the first flow path 11 in the first fluid outlet vicinity portion 11a is formed to be larger than the flow path width W11b in the portion 11b upstream of the first fluid outlet vicinity portion 11a. Therefore, the channel cross-sectional area S11a is made larger than the channel cross-sectional area S11b.
  • first fluid outlet vicinity portion 11a refers to the end portion on the outlet side (here, the first inlet / outlet pipe 4a side) from the inlet side (here, the end part on the first inlet / outlet pipe 4b side) of the first flow path 11.
  • the portion having a channel length of 20 to 50% closer to the outlet side among the channel lengths up to).
  • the number of flow paths in the first fluid outlet vicinity portion 11a is larger than the number of flow paths in the portion upstream of the first fluid outlet vicinity portion 11a.
  • the first flow paths 11 may be merged so as to reduce the number.
  • two first flow paths 11 adjacent to each other in the arrangement direction of the first flow paths 11 are merged at the first fluid outlet vicinity portion 11a to form one, and then after the merge.
  • the flow path width W11a in the first fluid outlet vicinity part 11a may be formed to be larger than the sum of the flow path widths W11b in the upstream part 11b of the first fluid outlet vicinity part 11a before joining. .
  • the flow path cross-sectional area S11a in the first fluid outlet vicinity part 11a after the merge is made larger than the sum of the flow path cross-sectional areas S11b in the portion 11b upstream of the first fluid outlet vicinity part 11a before the merge. be able to.
  • the flow passage cross-sectional area S11a in the first fluid outlet vicinity portion 11a of the first flow passage 11 is larger than the upstream portion 11b. While limiting the decrease in the heat transfer coefficient due to the decrease in the flow velocity of the first fluid in the first flow path 11 to the first fluid outlet vicinity portion 11a, the scale that deposits when the first fluid is heated is in the vicinity of the first fluid outlet. It is possible to prevent clogging of the portion 11a.
  • the first flow in the water heat exchanger 1 can be obtained not only in this embodiment and the same effects as those of the first to fourth modifications, but also with a minimum decrease in the heat transfer coefficient. Clogging of the path 11 can be suppressed.
  • the flow passage cross-sectional area S21a in the second fluid outlet vicinity portion 21a located in the vicinity is formed to be larger than the flow passage cross-sectional area S21b in the portion 21b upstream of the second fluid outlet vicinity portion 21a.
  • the channel width W21a of the second channel 21 in the second fluid outlet vicinity portion 21a is formed to be larger than the channel width W21b in the portion 21b upstream of the second fluid outlet vicinity portion 21a. Therefore, the channel cross-sectional area S21a is made larger than the channel cross-sectional area S21b.
  • the second fluid outlet vicinity portion 21a refers to the end portion on the outlet side (here, the second inlet / outlet tube 5b side) from the inlet side (here, the end portion on the second inlet / outlet tube 5a side) of the second flow path 21.
  • the second flow path 21 as in the above-described modification 4 is divided into a plurality of flow path groups 21A, 21B, and 21C, and these flow path groups 21A, 21B, and 21C are connected in series.
  • a configuration in which the flow path width W21a of the second flow path 21 in the second fluid outlet vicinity 21a can be increased.
  • the channel group 21A located in the vicinity of the second fluid outlet is a second fluid outlet vicinity part 21a
  • the channel groups 21B and 21C are the second fluid outlet vicinity part.
  • the channel width W21a of the second channel 21 constituting the channel group 21A constituting the channel group 21A is set to the second channel 21 constituting the channel groups 21B and 21C. What is necessary is just to form so that it may become larger than flow-path width W21b.
  • the number of flow paths in the second fluid outlet vicinity portion 21a is larger than the number of flow paths in the portion upstream of the second fluid outlet vicinity portion 21a.
  • the second flow path 21 may be merged so as to reduce the number.
  • the two second flow paths 21 adjacent in the arrangement direction of the second flow paths 21 are merged at the second fluid outlet vicinity portion 21a so as to become one.
  • the channel width W21a in the second fluid outlet vicinity portion 21a may be formed to be larger than the total of the channel width W21b in the upstream portion 21b of the second fluid outlet vicinity portion 21a before joining. .
  • the flow path cross-sectional area S21a in the second fluid outlet vicinity part 21a after the merge is made larger than the total of the flow path cross-sectional areas S21b in the portion 21b upstream of the second fluid outlet vicinity part 21a before the merge. be able to.
  • the flow path group 21A located near the outlet of the second fluid is the second fluid outlet vicinity part 21a, and the flow path groups 21B and 21C are the upstream part 21b of the second fluid outlet vicinity part 21a.
  • the number N21a of the second flow paths 21 constituting the flow path group 21A may be made larger than the number N21b of the flow paths 21B and 21C.
  • the channel widths W21a, W21b (channel cross-sectional areas S21a, S21b) of the second channels 21 are the same, and the channel cross-sectional area S21a in the channel group 21A can be changed by changing the number of channels.
  • the total of the channel cross-sectional areas S21b in the channel groups 21B and 21C is changed.
  • the second channel 21 has a larger channel cross-sectional area S21a in the second fluid outlet vicinity portion 21a than the upstream portion 21b,
  • the second fluid containing a large amount of gas components that increase with evaporation while limiting the decrease in the heat transfer coefficient due to the decrease in the flow rate of the second fluid in the second flow path 21 to only the second fluid outlet vicinity 21a. It can flow smoothly through the outlet vicinity 21a.
  • the second flow in the water heat exchanger 1 can be obtained not only in this embodiment and the same effects as those of the first to fifth modifications, but also with a minimum decrease in the heat transfer coefficient. An increase in pressure loss in the passage 21 can be suppressed.
  • the second number in the water heat exchanger 1 is increased.
  • the number of flow paths in the vicinity of the inlet of the second fluid is reduced, so that the distribution performance of the second fluid in the second flow path 21 can be kept good.
  • the present invention includes a first layer in which a plurality of first flow paths through which water as a first fluid flows, a second layer in which a plurality of second flow paths through which a refrigerant as a second fluid flows, Are laminated, and can be widely applied to a water heat exchanger that performs heat exchange between the first fluid and the second fluid.

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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

Dans la présente invention, des premiers canaux (11) s'étendent à partir d'une section d'extrémité d'une première couche (10) jusqu'à une autre section d'extrémité de celle-ci dans une direction qui croise la direction dans laquelle les premiers canaux (11) sont disposés, lorsqu'on observe la première couche (10) dans la direction de superposition en couches. Des seconds canaux (21) s'étendent à partir d'une section d'extrémité d'une seconde couche (20) jusqu'à une autre section d'extrémité de celle-ci dans une direction qui croise la direction dans laquelle les seconds canaux (21) sont disposés, lorsqu'on observe la seconde couche (20) dans la direction de superposition en couches. Ici, les premiers canaux (11) possèdent une forme tortueuse lorsqu'on observe la première couche (10) dans la direction de superposition en couches, et/ou les seconds canaux (21) possèdent une forme tortueuse lorsqu'on observe la seconde couche (20) dans la direction de superposition en couches.
PCT/JP2018/000309 2017-01-13 2018-01-10 Échangeur thermique à eau WO2018131596A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP18738883.0A EP3569962B1 (fr) 2017-01-13 2018-01-10 Échangeur thermique à eau
US16/477,705 US20190360758A1 (en) 2017-01-13 2018-01-10 Water heat exchanger
CN201880006479.6A CN110168300B (zh) 2017-01-13 2018-01-10 水热交换器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017-004638 2017-01-13
JP2017004638A JP6432613B2 (ja) 2017-01-13 2017-01-13 水熱交換器

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WO2018131596A1 true WO2018131596A1 (fr) 2018-07-19

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US (1) US20190360758A1 (fr)
EP (1) EP3569962B1 (fr)
JP (1) JP6432613B2 (fr)
CN (1) CN110168300B (fr)
WO (1) WO2018131596A1 (fr)

Citations (6)

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EP3569962A4 (fr) 2020-09-02
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CN110168300B (zh) 2021-08-24
CN110168300A (zh) 2019-08-23
US20190360758A1 (en) 2019-11-28
JP6432613B2 (ja) 2018-12-05
JP2018112381A (ja) 2018-07-19

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