WO2021140611A1 - Échangeur de chaleur à plaques, dispositif de pompe à chaleur doté d'un échangeur de chaleur à plaques et système de chauffage du type à pompe à chaleur doté du dispositif de pompe à chaleur - Google Patents

Échangeur de chaleur à plaques, dispositif de pompe à chaleur doté d'un échangeur de chaleur à plaques et système de chauffage du type à pompe à chaleur doté du dispositif de pompe à chaleur Download PDF

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Publication number
WO2021140611A1
WO2021140611A1 PCT/JP2020/000458 JP2020000458W WO2021140611A1 WO 2021140611 A1 WO2021140611 A1 WO 2021140611A1 JP 2020000458 W JP2020000458 W JP 2020000458W WO 2021140611 A1 WO2021140611 A1 WO 2021140611A1
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WO
WIPO (PCT)
Prior art keywords
plate
heat transfer
contact surface
heat exchanger
heat
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Application number
PCT/JP2020/000458
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English (en)
Japanese (ja)
Inventor
発明 孫
寿守務 吉村
佳峰 永島
匠 白石
亮輔 安部
政博 横井
伊東　大輔
Original Assignee
三菱電機株式会社
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.)
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Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2021569662A priority Critical patent/JP7270776B2/ja
Priority to PCT/JP2020/000458 priority patent/WO2021140611A1/fr
Publication of WO2021140611A1 publication Critical patent/WO2021140611A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/06—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being attachable to the element

Definitions

  • the present disclosure relates to a plate heat exchanger equipped with inner fins, a heat pump device equipped with a plate heat exchanger, and a heat pump heating system equipped with a heat pump device.
  • Patent Document 1 As a heat exchanger provided with an inner fin.
  • the inner fin of Patent Document 1 is arranged in the exhaust passage, and is formed so that the cross-sectional shape seen from the distribution direction of the exhaust is rectangular wavy, and the wavy side surface portion is offset in the direction of continuous waves.
  • This is an offset type fin in which a plurality of segments are formed.
  • a triangular cut-up portion protruding inward in a wavy shape is formed, and one cut-up portion is formed for each segment and is inclined with respect to the flow direction of the exhaust gas. It is formed in this way.
  • Patent Document 1 a triangular cut-up portion is provided in one segment, and it is stated that this cut-up portion can form a vortex in the exhaust flow to improve heat transfer performance.
  • the cut-up portion is formed so as to be inclined with respect to the flow direction of the exhaust gas, there is a problem that the pressure loss of the fluid increases.
  • the present disclosure has been made in view of these points, and is a plate-type heat exchanger capable of improving heat transfer performance while reducing pressure loss, a heat pump device equipped with a plate-type heat exchanger, and a heat pump device. It is an object of the present invention to provide a heat pump type heating system equipped with a heat pump device.
  • the plate-type heat exchanger is a plate-type heat exchanger in which a flow path is formed by each space between a plurality of laminated heat transfer plates and inner fins are arranged in the flow path.
  • the flow direction of the fluid is the first direction
  • the direction orthogonal to the first direction is the second direction
  • the stacking direction of the heat transfer plates is the third direction.
  • the inner fin has a side surface extending in the third direction and a contact surface joined to the heat transfer plate, and the width W of the contact surface in the second direction is larger than the height H of the side surface in the third direction.
  • the contact surface is provided with a first opening having a length L in the second direction and a height H or more in the third direction on the side surface.
  • the width W of the contact surface in the second direction is larger than the height H of the side surface in the third direction, so that the width W of the contact surface is larger than the height H of the side surface in the third direction.
  • the density of the side surface of the inner fin is reduced, and the pressure loss can be reduced.
  • the contact surface is provided with the first opening having a length L in the second direction equal to or higher than a height H in the third direction on the side surface, the heat transfer area is equal to the inner wall surface of the first opening. Can be increased, and heat transfer performance can be improved.
  • FIG. 1 is a front view of the 1st heat transfer plate of the plate type heat exchanger 100 which concerns on Embodiment 1.
  • FIG. 2nd heat transfer plate of the plate type heat exchanger 100 which concerns on Embodiment 1.
  • FIG. It is sectional drawing which cut the fin part of the laminated part which laminated two heat transfer sets 200 of the plate type heat exchanger 100 which concerns on Embodiment 1 at the position AA of FIG.
  • FIG. is sectional drawing which cut the header part of the laminated part which laminated two heat transfer sets 200 of the plate type heat exchanger 100 which concerns on Embodiment 1 at the position BB of FIG.
  • FIG. 8 is a cross-sectional view taken along the line AA of FIG. It is a front shape view of the slit part of the inner fin 4 of the plate type heat exchanger 100 which concerns on Embodiment 1.
  • FIG. 13 is a cross-sectional view taken along the line AA of FIG. It is sectional drawing of a part of the component part which joined the inner fin 4 between the 1st heat transfer plate 1 and the 2nd heat transfer plate 2 of the plate type heat exchanger 100 which concerns on Embodiment 2.
  • FIG. 13 is a cross-sectional view taken along the line AA of FIG. It is sectional drawing of a part of the component part which joined the inner fin 4 between the 1st heat transfer plate 1 and the 2nd heat transfer plate 2 of the plate type heat exchanger 100 which concerns on Embodiment 2.
  • FIG. 17 is a cross-sectional view taken along the line AA of FIG.
  • FIG. 17 is a cross-sectional view taken along the line BB of FIG.
  • FIG. 5 is a fluid flow distribution diagram in the plate heat exchanger 100 according to the third embodiment.
  • FIG. 22 is a cross-sectional view taken along the line AA of FIG.
  • FIG. 22 is a cross-sectional view taken along the line BB of FIG.
  • FIG. 5 is a cross-sectional view of a part of a component portion in which an inner fin 4 is joined between a first heat transfer plate 1 and a second heat transfer plate 2 of the plate heat exchanger 100 of the pattern 1 according to the fifth embodiment.
  • FIG. 22 is a cross-sectional view taken along the line AA of FIG.
  • FIG. 22 is a cross-sectional view taken along the line BB of FIG.
  • FIG. 5 is a cross-sectional view of a part of a component portion in which an inner fin 4 is joined between a first heat transfer plate 1 and a second heat transfer plate 2 of the plate heat exchanger 100 of the pattern 1 according to the fifth embodiment.
  • FIG. 5 is a cross-sectional view of a part of a component portion in which an inner fin 4 is joined between a first heat transfer plate 1 and a second heat transfer plate 2 of the plate heat exchanger 100 of the pattern 2 according to the fifth embodiment. It is sectional drawing of a part of the component part which joined the inner fin 4 between the 1st heat transfer plate 1 and the 2nd heat transfer plate 2 of the plate type heat exchanger 100 which concerns on Embodiment 6. It is a perspective view of a part of the inner fin 4 of the plate type heat exchanger 100 which concerns on Embodiment 6. It is a front view of the inner fin 4 of the plate type heat exchanger 100 which concerns on Embodiment 6.
  • FIG. 29 is a cross-sectional view taken along the line AA of FIG.
  • FIG. 29 is a cross-sectional view taken along the line BB of FIG. 29. It is a schematic diagram which shows the structure of the heat pump type heating system provided with the plate type heat exchanger 100 which concerns on Embodiment 7.
  • FIG. 1 is an exploded perspective view of the plate heat exchanger 100 according to the first embodiment.
  • FIG. 2 is a front view of the first heat transfer plate of the plate heat exchanger 100 according to the first embodiment.
  • FIG. 3 is a front view of the second heat transfer plate of the plate heat exchanger 100 according to the first embodiment.
  • FIG. 4 is a cross-sectional view in which the fin portion of the laminated portion in which two heat transfer sets 200 of the plate heat exchanger 100 according to the first embodiment are laminated is cut at the position AA in FIG.
  • FIG. 5 is a cross-sectional view in which the header portion of the laminated portion in which two heat transfer sets 200 of the plate heat exchanger 100 according to the first embodiment are laminated is cut at the position BB in FIG.
  • FIG. 1 is an exploded perspective view of the plate heat exchanger 100 according to the first embodiment.
  • FIG. 2 is a front view of the first heat transfer plate of the plate heat exchanger 100 according to the first embodiment.
  • FIG. 3 is a front view of
  • FIG. 6 is a cross-sectional view of the header portion of the laminated portion in which two heat transfer sets 200 of the plate heat exchanger 100 according to the first embodiment are laminated and cut at the position CC of FIG.
  • FIG. 7 is a perspective view of a part of the inner fins 4 of the plate heat exchanger 100 according to the first embodiment.
  • FIG. 8 is a front view of a part of the inner fins 4 of the plate heat exchanger 100 according to the first embodiment.
  • FIG. 9 is a cross-sectional view taken along the line AA of FIG.
  • FIG. 10 is a front view of the slit portion of the inner fin 4 of the plate heat exchanger 100 according to the first embodiment.
  • the plate-type heat exchanger 100 of the first embodiment has a configuration in which the first heat transfer plate 1 and the second heat transfer plate 2 are alternately laminated, and adjacent heat transfer plates 1 are laminated.
  • a flow path is formed by the space between the plates.
  • the flow paths arranged in the stacking direction alternate between the first flow path 6 through which the first fluid flows and the second flow path 7 through which the second fluid flows.
  • An inner fin 4 is arranged in the first flow path 6, and an inner fin 5 is arranged in the second flow path 7. In this way, the inner fin 4, the first heat transfer plate 1, the inner fin 5, and the second heat transfer plate 2 are laminated in this order from the front to form the heat transfer set 200.
  • the first heat transfer plate 1, the second heat transfer plate 2, the inner fins 4 and the inner fins 5 are each formed in a long plate shape.
  • the plate heat exchanger 100 is configured by stacking a plurality of heat transfer sets 200, and exchanges heat between the first fluid flowing through the first flow path 6 and the second fluid flowing through the second flow path 7. Do.
  • the contact portions between the laminated heat transfer sets 200 are joined by brazing or the like, and the plate heat exchanger 100 is configured as a rectangular parallelepiped as a whole.
  • the first fluid is, for example, water or brine solution.
  • the first fluid passes through in a liquid state and carries heat by sensible heat.
  • the second fluid is, for example, the refrigerants R410A, R32, R290, HFOmix, CO 2 and the like.
  • the second fluid transfers the latent heat of phase change such as gas and liquid to the first fluid by evaporating or condensing in the flow path.
  • the dotted arrow indicates the first fluid and the solid arrow indicates the second fluid.
  • the fluid flow method shows a countercurrent type in which the first fluid and the second fluid flow in opposite directions to each other, but the first embodiment is not limited to this flow method. ..
  • the fluid flow method may be a parallel flow type in which the first fluid and the second fluid flow in the same direction.
  • the operating pressure on the first fluid side is the pressure of the pump that flows the first fluid, and it is always operated at a low pressure. Further, the operating pressure on the second fluid side is the saturation pressure of the second fluid, and the operation is always performed at a high pressure.
  • first reinforcing side plate 3 and the second reinforcing side plate 12 are arranged on the outermost surface of the heat transfer set 200 in the stacking direction.
  • the plate laminated on the foremost surface is the first reinforcing side plate 3
  • the plate laminated on the rearmost surface is the second reinforcing side plate 12.
  • first reinforcing side plate 3 and the second reinforcing side plate 12 are formed in a long plate shape as shown in FIG. 1, and the corners of the four corners are formed in an R shape.
  • Circular holes serving as fluid inlets or outlets are formed at the four corners of the first reinforcing side plate 3.
  • a cylindrical inflow pipe or outflow pipe is provided on the periphery of each hole. Specifically, a first inflow pipe 9 into which the first fluid flows is provided in the lower left of the first reinforcing side plate 3, and a first outflow pipe in which the first fluid flows out is provided in the upper left of the first reinforcing side plate 3. 10 is provided.
  • a second inflow pipe 11 into which the second fluid flows is provided in the upper right of the first reinforcing side plate 3, and a second outflow pipe in which the second fluid flows out is provided in the lower right of the first reinforcing side plate 3. 8 is provided.
  • FIG. 1 shows a configuration in which the wall thickness of the side plate is uniformly uniform over the entire surface, but the configuration is not limited to the uniform configuration.
  • the wall thickness of the side plate near the inflow pipe and the outflow pipe may be thicker than the wall thickness of other parts.
  • the inflow pipe and the outflow pipe show the same size, but the size is not limited to this, and the size does not have to be the same.
  • the first heat transfer plate 1 is provided with a first inflow hole 13 into which the first fluid flows in, and a first outflow hole 14 in which the first fluid flows out in the upper left. Is provided.
  • a second inflow hole 15 into which the second fluid flows is provided in the upper right of the first heat transfer plate 1, and a second outflow hole 16 in which the second fluid flows out is provided in the lower right.
  • a cylindrical peripheral wall W is provided around the second inflow hole 15 and the second outflow hole 16, and the second inflow hole 15 and the second outflow hole 16 are the first. It is configured so that it does not communicate with the flow path 6. As a result, the inflow of the second fluid from the second inflow hole 15 and the second outflow hole 16 into the first flow path 6 is blocked.
  • the second heat transfer plate 2 is provided with a first inflow hole 17 into which the first fluid flows in, and a first outflow hole 18 in which the first fluid flows out is provided in the upper left.
  • a second inflow hole 19 into which the second fluid flows is provided in the upper right of the second heat transfer plate 2, and a second outflow hole 20 in which the second fluid flows out is provided in the lower right.
  • a cylindrical peripheral wall W is provided around the first inflow hole 17 and the first outflow hole 18, and the first inflow hole 17 and the first outflow hole 18 are second. It is configured so that it does not communicate with the flow path 7. As a result, the inflow of the first fluid from the first inflow hole 17 and the first outflow hole 18 into the second flow path 7 is blocked.
  • heat transfer plate When it is not necessary to distinguish between the first heat transfer plate 1 and the second heat transfer plate 2, they are collectively referred to as "heat transfer plate”. When it is not necessary to distinguish between the first reinforcing side plate 3 and the second reinforcing side plate 12, they are collectively referred to as “side plates”. When it is not necessary to distinguish between the first flow path 6 and the second flow path 7, they are collectively referred to as "flow path”.
  • the flow direction of the fluid that is, the vertical direction in FIG. 1
  • the direction orthogonal to the first direction that is, the left-right direction in FIG. 1
  • the direction orthogonal to the first direction and the second direction, and the stacking direction of the heat transfer plates is referred to as the third direction.
  • the heat transfer plate has a flat portion 22 and an outer wall portion 23 extending outward from both ends of the flat portion 22 in the second direction, and the outer wall of the heat transfer plate adjacent to the third direction.
  • the parts 23 are in contact with each other.
  • a space is formed between the adjacent flat portions 22, and this space serves as the first flow path 6 or the second flow path 7.
  • the first flow path 6 is between the two heat transfer sets 200
  • the second flow path 7 is between the first heat transfer plate 1 and the second heat transfer plate 2.
  • header portions 21 are provided at both ends of the heat transfer plate in the first direction.
  • the inner fin 4 has the same height H (see FIG. 9) as the flow path height l 1 (see FIG. 4) of the first flow path 6, and the flat portion 22 and the second transfer of the first heat transfer plate 1. It is in contact with the flat portion 22 of the heat plate 2. The contact portion may or may not be joined by brazing or the like, but will be described below as being joined.
  • the inner fin 5 has the same height as the flow path height l 2 (see FIG. 4) of the second flow path 7, and is formed by the flat portion 22 of the first heat transfer plate 1 and the second heat transfer plate 2. It is in contact with the flat portion 22.
  • the height H of the inner fin 4 is made higher than the height of the inner fin 5, but the heights thereof may be the same or may be reversed.
  • the inner fin 4 has a side surface 24 extending in the third direction and a contact surface 25 in contact with the heat transfer plate. More specifically, the inner fin 4 is composed of offset fins. That is, in the inner fin 4, the side surface 24 and the contact surface 25 are alternately connected in the second direction, and the corrugated portions formed into a waveform are alternately formed by arranging a plurality of corrugated portions in the first direction with a deviation of half a wave.
  • the contact surface 25 is formed in a rectangular shape when viewed from the front, and the width W in the second direction (see FIG. 9) is larger than the height H in the third direction of the side surface 24. It is largely configured.
  • the density of the side surface 24 is lower than that in which the width W of the contact surface 25 in the second direction is smaller than the height H of the side surface 24 in the third direction.
  • the height H of the side surface 24 is lower than the width W in the second direction, the pressure resistance performance can be improved as compared with the case where the height H is higher than the width W.
  • the contact surface 25 is formed in a quadrangular shape when viewed from the front, the shape is not limited to this. When the contact surface 25 has a shape other than a quadrangle, the maximum width of the contact surface 25 in the second direction is larger than the height H of the side surface 24 in the third direction.
  • the contact surface 25 is provided with a first opening 26 having a length L in the second direction and a height H or more of the side surface 24.
  • the first opening 26 is formed so that the length L in the second direction is larger than the length D in the first direction.
  • the contact surface 25 is formed in a quadrangular shape that is long in the second direction
  • the first opening 26 is also formed in a quadrangular shape that is long in the second direction, in other words, in a slit shape, in accordance with the shape of the contact surface 25.
  • the first opening 26 may have the same length in the first direction and the second direction.
  • the shape of the first opening 26 is not limited to a quadrangle, and may be any one shape such as a circle, a triangle, a polygon, a D shape, an arrow shape, or a plurality of shapes shown in FIG. It may be provided in combination of shapes.
  • FIG. 10 shows an example of a pentagon as an example of a polygon, and an example of a plank arrow shape and a concave arrow shape as arrow shapes.
  • FIG. 7 shows a configuration in which all the contact surfaces 25 have a width W larger than the height H, but the inner fin 4 includes a contact surface 25 having a width W smaller than the height H. You may be.
  • the first opening 26 is formed in the contact surface 25 portion having a width W larger than the height H. That is, the inner fin 4 has a contact surface in which the width W in the second direction is larger than the height H in the stacking direction of the side surface 24, and the first opening 26 is formed in the contact surface.
  • the width W of the contact surface 25 is set in the range of 2 to 5 times the height H of the side surface 24. Further, it is desirable that the width W of the contact surface 25 satisfies H ⁇ WL ⁇ 3H in order to maintain the joint strength between the contact surface 25 and the flat portion 22 of the heat transfer plate.
  • the width W of the contact surface 25 is set so as to satisfy this relationship and the first opening 26 is provided at the center of the contact surface 25 in the second direction, both sides of the first opening 26 in the second direction, A joint surface having a width of 0.5 to 1.5H can be formed. Therefore, the joint strength between the contact surface 25 and the flat portion 22 of the heat transfer plate is maintained, and the heat exchange between the inner fin 4 and the heat transfer plate can be sufficiently performed.
  • the first fluid that has flowed into the first inflow pipe 9 of the first fluid from the outside flows into the first flow path 6 through the first inflow hole 13 of the first fluid.
  • the first fluid flowing into the first flow path 6 gradually spreads toward the outer wall portions 23 at both ends of the first heat transfer plate 1 in the second direction, and the inner fins 4 are directed upward as shown in FIG. It flows through the first fluid and flows out from the first outflow pipe 10 of the first fluid through the first outflow hole 14 of the first fluid.
  • a second fluid flows through the second flow path 7, and the heat of the second fluid is transferred to the first heat transfer plate 1 or the second heat transfer plate 2, and as a result, the first fluid and the second fluid Heat exchange with.
  • the inner fin of the first embodiment does not have a portion corresponding to the cut-up portion of the conventional structure, and corresponds to a configuration in which only the first opening 26 is provided. Therefore, in the inner fin of the first embodiment, it is possible to prevent the first fluid flowing in the first flow path 6 from colliding with the cut-up portion, and it is possible to reduce the pressure loss in the flow direction of the first fluid.
  • the first fluid directly contacts the first heat transfer plate 1 or the second heat transfer plate 2 without passing through the inner fin 4. Therefore, the heat exchange performance is also improved.
  • the width W of the contact surface 25 is made larger than the height H of the side surface 24, so that the area of the contact surface 25 is expanded as compared with the configuration smaller than the height H of the side surface 24. Therefore, the first opening 26 provided on the contact surface 25 can also be largely secured. Since the inner wall surface of the first opening 26 serves as a heat transfer surface, the heat transfer area can be increased by securing a large first opening 26, and the heat transfer performance can be improved to improve the heat exchange performance. it can.
  • FIG. 11 shows the results of calculating the changes in the pressure loss ratio and the heat transfer performance ratio between the case where the width W of the contact surface 25 is increased and the case where the contact surface 25 is provided with an opening.
  • FIG. 11 is a diagram showing the calculation results of the pressure loss ratio and the heat transfer performance ratio of the inner fins of the plate heat exchanger 100 of the first embodiment.
  • the pressure loss ratio [%] is shown as a bar graph
  • the heat transfer performance ratio [%] is shown as a line graph.
  • the “base” is a case where the width W of the contact surface 25 of the inner fin 4 is set to a certain width.
  • “Medium fin width” is a case where the width W of the “base” is set to 100% and the width W is increased to 133%.
  • “Large fin width” is a case where the width W of the “base” is set to 100% and the width W is increased to 189%.
  • “Large fin width (with opening)” is a case where the width W of the contact surface 25 is “large fin width” and the first opening 26 is provided on the contact surface 25.
  • the pressure loss ratio is reduced by increasing the width W of the contact surface 25.
  • the "large fin width (with opening)" has almost the same or slightly improved pressure loss ratio as compared with the "large fin width” in which the first opening 26 is not provided.
  • the "large fin width (with opening)” is improved as compared with the "large fin width” in which the first opening 26 is not provided. That is, from FIG. 11, by increasing the width W of the contact surface 25 of the inner fin 4 and providing the first opening 26 on the increased contact surface, the pressure loss ratio is reduced and the heat transfer performance ratio is improved. I know I can do it.
  • the inner fin 4 is shown to use an offset fin here, the inner fin 4 is not limited to the offset fin.
  • the inner fin 4 may be any one or a combination of a flat plate fin type, a wavy fin type, a louver type, and a corrugated fin type.
  • the inner fin of the first embodiment has a contact surface 25 having a width W larger than the height H of the side surface 24, and a length L in the second direction is equal to or larger than the height H of the side surface 24.
  • the configuration may be such that the first opening 26 of the above is formed.
  • the inner fin 5 may have the above configuration. Further, both the inner fin 4 and the inner fin 5 may have the above configuration. When both the inner fins 4 and the inner fins 5 have the above configuration, the heat transfer properties of both the first flow path 6 and the second flow path 7 can be further improved, and as a result, the performance of the plate heat exchanger 100 can be improved. Can be improved.
  • the first embodiment is a plate heat exchanger in which a flow path is formed by each space between a plurality of laminated heat transfer plates and inner fins are arranged in the flow path.
  • the flow direction of the fluid in the flow path is the first direction
  • the direction orthogonal to the first direction is the second direction
  • the stacking direction of the heat transfer plates is the third direction.
  • the inner fin has a side surface extending in the third direction and a contact surface 25 joined to the heat transfer plate, and the width W of the contact surface 25 in the two directions is larger than the height H of the side surface in the third direction.
  • the contact surface 25 is provided with a first opening having a length L in the second direction and a height H or more in the third direction on the side surface.
  • the width W of the contact surface 25 in the two directions is configured to be larger than the height H of the side surface in the third direction, and the length L of the contact surface 25 in the second direction is the third direction of the side surface.
  • the first opening 26 is provided at the center of the contact surface 25 in the second direction, and the width W of the contact surface 25 is 2 to 5 times the height H of the side surface. It is a range, and the length L of the first opening 26 in the second direction is used to satisfy H ⁇ WL ⁇ 3H.
  • joint surfaces having a width of 0.5 to 1.5H can be formed on both sides of the first opening 26 in the second direction. Therefore, the joint strength between the contact surface 25 and the heat transfer plate is maintained, and heat exchange between the inner fin 4 and the heat transfer plate can be sufficiently performed on the contact surface.
  • Embodiment 2 Hereinafter, the second embodiment will be described, but the description of the parts overlapping with the first embodiment will be omitted, and the same parts or the corresponding parts as those of the first embodiment will be designated by the same reference numerals.
  • FIG. 12 is a perspective view of a part of the inner fins 4 of the plate heat exchanger 100 according to the second embodiment.
  • FIG. 13 is a front view of a part of the inner fins 4 of the plate heat exchanger 100 according to the second embodiment.
  • FIG. 14 is a cross-sectional view taken along the line AA of FIG.
  • FIG. 15 is a cross-sectional view of a part of a component portion in which the inner fin 4 is joined between the first heat transfer plate 1 and the second heat transfer plate 2 of the plate heat exchanger 100 according to the second embodiment. ..
  • the inner fins 4 of the plate heat exchanger 100 according to the second embodiment have a configuration in which protrusions 27a and 27b extending in the third direction are formed at both ends of the first opening 26 in the second direction. Have.
  • the protruding portion 27a and the protruding portion 27b are parallel to the side surface 24 of the inner fin 4.
  • the method of forming the projecting portion 27a and the projecting portion 27b is arbitrary, but is formed by, for example, cutting up from the contact surface 25.
  • the protruding portion 27a and the protruding portion 27b By providing the protruding portion 27a and the protruding portion 27b on the inner fin 4 in this way, the heat transfer area can be increased, so that the heat transfer performance can be improved. Further, since each of the protruding portion 27a and the protruding portion 27b is formed parallel to the side surface 24 of the inner fin 4, it is possible to suppress an increase in the pressure loss of the first fluid.
  • the tip 28 of each of the protrusion 27a and the protrusion 27a is the first heat transfer plate 1 or the first. 2 It is in contact with the heat transfer plate 2.
  • the tip 28 of each of the protrusion 27a and the protrusion 27a is in contact with the first heat transfer plate 1 or the second heat transfer plate 2, so that the inner fin 4 is in contact with the first heat transfer plate 1 or the second heat transfer plate 2 as compared with the case where they are not in contact.
  • the thermal resistance between the heat transfer plates can be reduced.
  • the contact portions between the tip portions 28 of the protrusions 27a and the protrusions 27a and the heat transfer plate may or may not be joined.
  • FIG. 16 is a diagram showing the calculation results of the pressure loss ratio and the heat transfer performance ratio of the inner fins of the plate heat exchanger 100 according to the second embodiment.
  • the pressure loss ratio [%] is shown as a bar graph
  • the heat transfer performance ratio [%] is shown as a line graph.
  • the “base” in FIG. 16 is the same as the “base” in FIG. 11, and the “large fin width (with the first opening)” in FIG. 16 is the “large fin width (with the first opening)” in FIG. Is similar to. In all of “Large fin width (with first opening)", “Large fin width (medium number of protruding parts)", and “Large fin width (large number of protruding parts)” in FIG.
  • the width W of the contact surface 25 is "fin”. It is constant at 189% of "wide", that is, "base”.
  • the number of protruding portions is a configuration in which the protruding portions 27a and the protruding portions 27b are provided in about half of all the first opening 26s of the inner fin 4.
  • the large number of protruding portions means that all the first openings 26 of the inner fin 4 are provided with the protruding portions 27a and the protruding portions 27b.
  • the inner fin 4 may be provided on the inner fin 5, or both the inner fin 4 and the inner fin 5 may be provided. Good.
  • the heat transfer performance is further improved by providing the protrusions 27a and the protrusions 27b extending in parallel to the side surface 24 at both ends of the first opening 26 in the second direction. Can be planned. Further, since the tip 28 of each of the protruding portion 27a and the protruding portion 27b is joined to the first heat transfer plate 1 or the second heat transfer plate 2, the thermal resistance between the inner fin and the heat transfer plate is reduced. be able to.
  • Embodiment 3 Hereinafter, the third embodiment will be described, but the description of the parts overlapping with the first to second embodiments will be omitted, and the same parts or the corresponding parts will be designated by the same reference numerals.
  • FIG. 17 is a cross-sectional view of a part of a component portion in which the inner fin 4 is joined between the first heat transfer plate 1 and the second heat transfer plate 2 of the plate heat exchanger 100 according to the third embodiment. ..
  • FIG. 18 is a cross-sectional view taken along the line AA of FIG.
  • FIG. 19 is a cross-sectional view taken along the line BB of FIG.
  • the height of the protrusion 27a and the protrusion 27b are the same, the third embodiment, the height H 2 of the height H 1 and the protruding portion 27b of the protruding portion 27a different.
  • the height H 1 of the protrusion 27a is shorter than the height H 2 of the protrusion 27b, but the reverse is also possible. Due to the structure in which the heights of the protrusions are different in this way, the drift in the flow path can be improved.
  • the inner fin 4 is in contact with the first heat transfer plate 1 and the second heat transfer plate 2 as compared with the case where they are not in contact with each other. And the thermal resistance of the first heat transfer plate 1 can be reduced.
  • the tip 28 of the protruding portion 27a is not in contact with the first heat transfer plate 1 and the second heat transfer plate 2. Therefore, the thermal resistance is increased as compared with the case of contact.
  • the heat transfer performance can be improved by increasing the heat transfer area. That is, since the tip 28 of the protrusion 27a is not in contact with the heat transfer plate facing the tip 28, a gap is formed between the tip 28 and the heat transfer plate, and the first fluid is formed in the gap. Passes. Therefore, the heat transfer area between the first fluid and the inner fin 4 and the heat transfer area between the first fluid and the heat transfer plate are increased by the area of the tip 28 of the protruding portion 27a. By increasing the heat transfer area in this way, the heat transfer performance can be improved.
  • FIG. 20 is a fluid flow distribution diagram when no protrusion is provided on the inner fin as a comparative example.
  • FIG. 21 is a fluid flow distribution diagram in the plate heat exchanger 100 according to the third embodiment.
  • the dark part indicates the part where the flow velocity is high, and the light part indicates the part where the flow velocity is slow.
  • the variation of the flow velocity distribution is reduced and the drift is improved in FIG. 21 provided with the protrusion 27a and the protrusion 27b as compared with FIG. I understand.
  • the same effects as those of the first to second embodiments can be obtained.
  • the protrusions 27a and the protrusions 27b extending in the third direction are provided at both ends of the first opening 26 in the second direction.
  • the heat transfer performance can be improved.
  • the uneven flow can be further improved by making the heights of the protruding portion 27a and the protruding portion 27b different.
  • the thermal resistance between the inner fin 4 and the heat transfer plate is reduced by configuring the tip 28 of the protrusion 27b to contact the heat transfer plate facing the tip 28. Can be done. Further, in the third embodiment, the heat transfer area can be increased by making the tip 28 of the protrusion 27a not in contact with the heat transfer plate facing the tip 28, and the heat transfer performance can be improved. Can be improved. From the above, the heat exchange performance of the plate heat exchanger 100 can be improved.
  • the inner fin 5 may have the above configuration, or both the inner fin 4 and the inner fin 5 may have the above configuration.
  • Embodiment 4 Hereinafter, the fourth embodiment will be described, but the description of the parts overlapping with the first to third embodiments will be omitted, and the same parts or the corresponding parts will be designated by the same reference numerals.
  • FIG. 22 is a cross-sectional view of a part of a component portion in which the inner fin 4 is joined between the first heat transfer plate 1 and the second heat transfer plate 2 of the plate heat exchanger 100 according to the fourth embodiment. ..
  • FIG. 23 is a cross-sectional view taken along the line AA of FIG.
  • FIG. 24 is a cross-sectional view taken along the line BB of FIG.
  • the height of the protrusion 27a and the protrusion 27b are the same, the fourth embodiment, the height H 2 of the height H 1 and the protruding portion 27b of the protruding portion 27a different. Further, in the fourth embodiment, the tip portions 28 of both protruding portions are not in contact with the heat transfer plate.
  • the same effects as those of the first to second embodiments can be obtained.
  • the protrusions 27a and 27b extending in the third direction are provided at both ends of the first opening 26 in the second direction.
  • the heat transfer performance can be improved.
  • the drifting portion can be improved by making the heights of the protruding portion 27a and the protruding portion 27b different.
  • the tip portions 28 of both the protruding portion 27a and the protruding portion 27b are not in contact with the heat transfer plate.
  • the heat transfer area between the first fluid and the inner fin 4 and the heat transfer area between the first fluid and the heat transfer plate are equal to the area of the tip 28 of both the protrusion 27a and the protrusion 27b, respectively. ,To increase.
  • the heat transfer performance can be improved. From the above, the heat exchange performance of the plate heat exchanger 100 can be improved.
  • the inner fin 5 may have the above configuration, or both the inner fin 4 and the inner fin 5 may have the above configuration.
  • Embodiment 5 Hereinafter, the fifth embodiment will be described, but the description of the parts overlapping with the first to fourth embodiments will be omitted, and the same parts or the corresponding parts will be designated by the same reference numerals.
  • FIG. 25 is a cross section of a part of a component in which the inner fin 4 is joined between the first heat transfer plate 1 and the second heat transfer plate 2 of the plate heat exchanger 100 of the pattern 1 according to the fifth embodiment. It is a figure.
  • FIG. 26 is a cross section of a part of a component in which the inner fin 4 is joined between the first heat transfer plate 1 and the second heat transfer plate 2 of the plate heat exchanger 100 of the pattern 2 according to the fifth embodiment. It is a figure.
  • the fifth embodiment corresponds to the embodiment in which the inner fins of the first to fourth embodiments are applied to the double wall heat exchanger.
  • a mode in which the inner fins of the fourth embodiment shown in FIGS. 22 to 24 are applied to the double wall plate heat exchanger will be described.
  • At least a part of the plurality of heat transfer plates is composed of a double plate in which two plates are partially joined.
  • one or both of the first heat transfer plate 1 and the second heat transfer plate 2 have a configuration in which two plates are partially joined.
  • FIG. 25 shows a configuration in which only the first heat transfer plate 1 is partially joined to two plates.
  • the first heat transfer plate 1 has a configuration in which the plate 1a and the plate 1b are partially joined.
  • FIG. 26 shows a configuration in which both the first heat transfer plate 1 and the second heat transfer plate 2 are partially joined by two plates.
  • the first heat transfer plate 1 has a structure in which the plate 1a and the plate 1b are partially joined
  • the second heat transfer plate 2 has a structure in which the plate 2a and the plate 2b are partially joined.
  • the black-painted portion 29 between the plates is a joint portion.
  • a microchannel is formed between the two plates, and the microfluidic is configured to communicate with the outside.
  • the double wall plate heat exchanger of the fifth embodiment is effective in a usage mode in which mixing of two kinds of fluids is desired, for example, a mode in which a flammable refrigerant is used as the fluid.
  • the first fluid that has flowed into the microchannel leaks to the outside through the microchannel. As a result, it is possible to notify the outside that a defect has occurred in the heat transfer plate.
  • the same effects as those of the first to fourth embodiments can be obtained, and the heat transfer plates are formed by partially joining the two plates to form two kinds of fluids. Mixing can be prevented.
  • Embodiment 6 Hereinafter, the sixth embodiment will be described, but the description of the parts overlapping with the first to fifth embodiments will be omitted, and the same parts or the corresponding parts will be designated by the same reference numerals.
  • FIG. 27 is a cross-sectional view of a part of a component portion in which the inner fin 4 is joined between the first heat transfer plate 1 and the second heat transfer plate 2 of the plate heat exchanger 100 according to the sixth embodiment.
  • FIG. 28 is a perspective view of a part of the inner fins 4 of the plate heat exchanger 100 according to the sixth embodiment.
  • FIG. 29 is a front view of the inner fin 4 of the plate heat exchanger 100 according to the sixth embodiment.
  • FIG. 30 is a cross-sectional view taken along the line AA of FIG. 29.
  • FIG. 31 is a cross-sectional view taken along the line BB of FIG. 29.
  • the plate heat exchanger 100 of the sixth embodiment uses water as a fluid, and even if the heat transfer plate is damaged when the water freezes in the plate heat exchanger 100, the first fluid and the second fluid And are not mixed.
  • the first heat transfer plate 1 is a double plate in which the plate 1a and the plate 1b are partially joined.
  • the inner fin 4 of the sixth embodiment is an offset fin as shown in FIGS. 28 and 29.
  • the inner fin 4 has a first contact surface 25a on the side joined to the first heat transfer plate 1 and a second contact surface 25a on the side joined to the second heat transfer plate 2. It has a contact surface 25b.
  • the inner fin 4, periodically in the first direction as shown in FIG. 29, become enlarged provided portion to the width W 1 to form the width of the second contact surface 25b in the width W in the second direction There is.
  • This shape better understanding for the contact surface portion of enlarged width W 1 in FIG. 28 and FIG. 29 (hereinafter, referred to as enlarged contact surface) are shown poppy nets with a thin dot.
  • a T-shaped continuously enlarged surface 30 is formed by combining with the portion shaded by dark dots in FIG. 29).
  • the space surrounded by the continuously expanding surface 30 and the first heat transfer plate 1 facing the continuously expanding surface 30 with the first flow path 6 interposed therebetween has a larger volume than the other portions. Therefore, each of the continuously expanding surface 30 and the first heat transfer plate 1 portion facing the continuously expanding surface 30 is easily damaged by applying a force in the third direction due to expansion due to freezing of water.
  • the plate 1a of the first heat transfer plate 1 is set to have a lower strength than the plate 1b and the second heat transfer plate 2. Therefore, when the plate 1a is damaged by freezing, the plate 1a is damaged first. Therefore, even if the damage occurs, it is possible to prevent the first fluid and the second fluid from mixing.
  • the second opening 30a which is larger than the first opening 26, on the continuously enlarged surface 30, it is possible to suppress a decrease in heat transfer property.
  • the first fluid directly contacts the second heat transfer plate 2 in the second opening 30a without passing through the inner fin 4. Therefore, deterioration of heat transfer performance can be suppressed. Further, by providing the second opening 30a, the heat transfer area can be increased by the amount of the inner wall surface of the second opening 30a, and the deterioration of the heat transfer performance can be suppressed from this point as well.
  • the configuration may be such that the second opening 30a is provided on the expansion contact surface.
  • the protruding portions 27a and the protruding portions 27b of the above-described second to fourth embodiments may be applied to the inner fin 4. As a result, the drift in the first flow path 6 can be suppressed.
  • the inner fin is an offset fin, and the corrugated portion formed into a waveform by alternately connecting the side surface 24 and the contact surface 25 in the second direction is deviated by half a wave and is the first. It has a configuration in which a plurality of pieces are arranged side by side in the direction and alternately formed.
  • the contact surface 25 has a first contact surface 25a joined to one of two heat transfer plates facing each other with the inner fins interposed therebetween and a second contact surface 25b joined to the other.
  • the inner fin has a shape in which a portion in which the width of the second contact surface 25b is expanded is provided periodically in the first direction, and the enlarged contact surface which is a portion in which the width of the second contact surface 25b is expanded is provided.
  • the other heat transfer plate in contact with the second contact surface 25b is composed of a double plate having two plates.
  • the portion where the width of the second contact surface 25b is expanded becomes a freeze-breaking place, and by using a double plate in the portion which becomes the freeze-breaking place, even if the heat transfer plate is damaged due to freezing, the first fluid And the second fluid can be prevented from mixing. Therefore, a highly reliable plate heat exchanger can be realized. Further, by providing the second opening 30a larger than the first opening 26 on the enlarged contact surface, the heat transfer area can be increased, and the deterioration of the heat transfer performance due to the provision of the enlarged contact surface can be reduced. Can be suppressed.
  • the continuous expansion surface 30 is formed by combining the second contact surface 25b and the expansion surface in one corrugated portion continuous on both sides of the expansion contact surface in the first direction.
  • the length D 1 in the first direction is equal to or greater than the length D in the first direction of the first opening
  • the length L 1 in the second direction is the length L 1 in the second direction in the second direction of the first opening.
  • a second opening having a length L or more is provided.
  • the heat transfer area can be further increased, and the deterioration of the heat transfer performance can be further suppressed.
  • the inner fin 5 may have the above configuration, or both the inner fin 4 and the inner fin 5 may have the above configuration.
  • Embodiment 7 Hereinafter, the seventh embodiment will be described, but the description of the parts overlapping with the first to sixth embodiments will be omitted, and the same parts or the corresponding parts will be designated by the same reference numerals.
  • the seventh embodiment describes the heat pump device equipped with the plate heat exchanger 100 described in the first to sixth embodiments.
  • a heat pump type heating system using a plate type heat exchanger as a condenser will be described as one of the usage forms of the heat pump device.
  • FIG. 32 is a schematic view showing the configuration of a heat pump type heating system including the plate type heat exchanger 100 according to the seventh embodiment.
  • the heat pump type heating system 300 includes a heat pump device 400 including a main refrigerant circuit 35 and a heat medium circuit 40.
  • the main refrigerant circuit 35 is a circuit in which the compressor 31, the second flow path of the heat exchanger 32, the expansion valve 33, and the heat exchanger 34 are sequentially connected, and the refrigerant circulates.
  • the heat medium circuit 40 is a circuit in which the first flow path of the heat exchanger 32, the heat medium utilization device 42, and the pump 41 are sequentially connected, and the heat medium circulates.
  • the compressor 31, the heat exchanger 32, the expansion valve 33, and the heat exchanger 34 are housed in the housing of the heat pump device 400.
  • the heat exchanger 32 is the plate type heat exchanger described in the above embodiment, and heat exchange between the refrigerant flowing through the main refrigerant circuit and the heat medium flowing through the heat medium circuit.
  • the heat medium used in the heat medium circuit 40 is, for example, water or brine liquid.
  • the refrigerant flowing through the main refrigerant circuit 35 is not particularly limited, and for example, the above-mentioned refrigerant can be used.
  • the double wall plate heat exchanger of the fifth embodiment is used as the heat exchanger 32. Then, a leak detection sensor 36 that detects a leak of the first fluid or the second fluid to the outside is installed in the heat pump device 400, and when a leak is detected, a buzzer is sounded to notify the outside, thereby achieving reliability.
  • a high heat pump type heating system can be realized.
  • the heat medium utilization device 42 is composed of an indoor heat exchanger of an air conditioner (not shown) that air-conditions the room.
  • the heat medium utilization device 42 heats the room by exchanging heat between the heat medium of the heat medium circuit 70 guided into the room and the room air.
  • the heat pump type heating system of the seventh embodiment includes the plate heat exchangers of the first to sixth embodiments, the heat exchange efficiency is good, the power consumption is suppressed, and the CO 2 emission can be reduced. A heat pump type heating system can be realized.
  • Plate heat exchangers are used in many industrial and household appliances such as heat pump hot water supply systems, heat pump cooling systems that use plate heat exchangers as evaporators, cooling chillers, power generators and food heat sterilization equipment. It can be used for equipment, etc.
  • the present disclosure can be used in a heat pump device that is easy to manufacture, can improve heat exchange performance, and needs to reduce power consumption.
  • 1 1st heat transfer plate 1a plate, 1b plate, 2 2nd heat transfer plate, 2a plate, 2b plate, 3 1st reinforcement side plate, 4 inner fins, 5 inner fins, 6 1st flow path, 7th 2 flow paths, 8 2nd outflow pipe, 9 1st inflow pipe, 10 1st outflow pipe, 11 2nd inflow pipe, 12 2nd reinforcing side plate, 13 1st inflow hole, 14 1st outflow hole, 15th 2 inflow hole, 16 second outflow hole, 17 first inflow hole, 18 first outflow hole, 19 second inflow hole, 20 second outflow hole, 21 header part, 22 flat part, 23 outer wall part, 24 side surface, 25 Contact surface, 25a 1st contact surface, 25b 2nd contact surface, 26 1st opening, 27a protruding part, 27b protruding part, 28 tip, 29 blackened part, 30 continuously enlarged surface, 30a 2nd opening, 31 Compressor, 32 heat exchanger, 33 expansion valve, 34 heat exchanger, 35 main ref

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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

Cet échangeur de chaleur de type à plaques est conçu pour avoir un passage d'écoulement qui est formé par des espaces respectifs entre une pluralité de plaques de transfert de chaleur empilées et comporte une ailette interne disposée dans le passage d'écoulement. Lorsque la direction d'un fluide s'écoulant à l'intérieur du passage d'écoulement est définie comme une première direction, la direction orthogonale à la première direction est définie comme une deuxième direction, et la direction qui est orthogonale aux première et deuxième directions et qui est la direction de stratification des plaques de transfert de chaleur est définie comme une troisième direction, l'ailette interne a une surface latérale s'étendant dans la troisième direction et une surface de contact qui est reliée aux plaques de transfert de chaleur. La surface de contact est façonnée sous une forme quadrilatérale, telle qu'elle est vue dans la troisième direction. La largeur (W) de la surface de contact dans la deuxième direction est supérieure à la hauteur (H) de la surface latérale dans la troisième direction. La surface de contact est pourvue d'une première ouverture dans laquelle la longueur (L) dans la deuxième direction est supérieure ou égale à la hauteur (H) de la surface latérale dans la troisième direction.
PCT/JP2020/000458 2020-01-09 2020-01-09 Échangeur de chaleur à plaques, dispositif de pompe à chaleur doté d'un échangeur de chaleur à plaques et système de chauffage du type à pompe à chaleur doté du dispositif de pompe à chaleur WO2021140611A1 (fr)

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JP2021569662A JP7270776B2 (ja) 2020-01-09 2020-01-09 プレート式熱交換器、プレート式熱交換器を備えたヒートポンプ装置、および、ヒートポンプ装置を備えたヒートポンプ式暖房システム
PCT/JP2020/000458 WO2021140611A1 (fr) 2020-01-09 2020-01-09 Échangeur de chaleur à plaques, dispositif de pompe à chaleur doté d'un échangeur de chaleur à plaques et système de chauffage du type à pompe à chaleur doté du dispositif de pompe à chaleur

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Application Number Priority Date Filing Date Title
PCT/JP2020/000458 WO2021140611A1 (fr) 2020-01-09 2020-01-09 Échangeur de chaleur à plaques, dispositif de pompe à chaleur doté d'un échangeur de chaleur à plaques et système de chauffage du type à pompe à chaleur doté du dispositif de pompe à chaleur

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61141586U (fr) * 1985-02-15 1986-09-01
JPH1123099A (ja) * 1997-07-02 1999-01-26 Showa Alum Corp 熱交換器
JP2007163047A (ja) * 2005-12-14 2007-06-28 Calsonic Kansei Corp ヒータコアの製造方法
WO2018088006A1 (fr) * 2016-11-14 2018-05-17 三菱電機株式会社 Échangeur de chaleur de type à plaques, dispositif de pompe à chaleur, système de chauffage de type pompe à chaleur/d'alimentation en eau chaude
WO2019176567A1 (fr) * 2018-03-15 2019-09-19 三菱電機株式会社 Échangeur de chaleur à plaques et dispositif de pompe à chaleur l'intégrant

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61141586U (fr) * 1985-02-15 1986-09-01
JPH1123099A (ja) * 1997-07-02 1999-01-26 Showa Alum Corp 熱交換器
JP2007163047A (ja) * 2005-12-14 2007-06-28 Calsonic Kansei Corp ヒータコアの製造方法
WO2018088006A1 (fr) * 2016-11-14 2018-05-17 三菱電機株式会社 Échangeur de chaleur de type à plaques, dispositif de pompe à chaleur, système de chauffage de type pompe à chaleur/d'alimentation en eau chaude
WO2019176567A1 (fr) * 2018-03-15 2019-09-19 三菱電機株式会社 Échangeur de chaleur à plaques et dispositif de pompe à chaleur l'intégrant

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