EP3882556A1 - Plattenwärmetauscher, wärmepumpenvorrichtung und kühlendes/erhitzendes heisswasserzufuhrsystem vom wärmepumpentyp - Google Patents

Plattenwärmetauscher, wärmepumpenvorrichtung und kühlendes/erhitzendes heisswasserzufuhrsystem vom wärmepumpentyp Download PDF

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Publication number
EP3882556A1
EP3882556A1 EP18940018.7A EP18940018A EP3882556A1 EP 3882556 A1 EP3882556 A1 EP 3882556A1 EP 18940018 A EP18940018 A EP 18940018A EP 3882556 A1 EP3882556 A1 EP 3882556A1
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EP
European Patent Office
Prior art keywords
flow passage
heat transfer
plate
projecting portion
projecting
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP18940018.7A
Other languages
English (en)
French (fr)
Other versions
EP3882556A4 (de
EP3882556B1 (de
Inventor
Faming SUN
Susumu Yoshimura
Yoshitaka EIJIMA
Sho SHIRAISHI
Ryosuke Abe
Masahiro Yokoi
Kazutaka Suzuki
Daisuke Ito
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP3882556A1 publication Critical patent/EP3882556A1/de
Publication of EP3882556A4 publication Critical patent/EP3882556A4/de
Application granted granted Critical
Publication of EP3882556B1 publication Critical patent/EP3882556B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/02—Domestic hot-water supply systems using heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the 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
    • 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
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like 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
    • F28F3/02—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
    • 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
    • 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
    • F28F3/10—Arrangements for sealing the margins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2240/00—Spacing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/106—Particular pattern of flow of the heat exchange media with cross flow
    • 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
    • F28F3/042—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 local deformations of the element
    • F28F3/044—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 local deformations of the element the deformations being pontual, e.g. dimples

Definitions

  • the present invention relates to a plate-type heat exchanger including an inner fin, to a heat pump device, and to a heat-pump-type cooling and heating hot-water supply system.
  • a stacked plate-type heat exchanger including a plurality of heat transfer plates stacked with an inner fin interposed therebetween, and is configured to allow different fluids to alternately flow through each flow passage formed between a heat transfer plate and a heat transfer plate, and also is configured to exchange heat via the heat transfer plates (see, for example, Patent Literature 1).
  • the plate-type heat exchanger has a cuboidal shape as a whole and, at both ends of the inner fin in a transverse direction, has gaps between the inner fin and wall surfaces erected from both ends of each of the heat transfer plates.
  • the presence of such gaps undesirably causes a fluid to preferentially flow into the gaps without flowing through the inner fin.
  • the wall surfaces in the gaps to inhibit the fluid from undesirably flowing into the gaps.
  • Patent Literature 1 Japanese Unexamined Patent Application Publication JP 2015-203508 A
  • Patent Literature 1 By providing the wall surfaces, Patent Literature 1 can inhibit the fluid from preferentially flowing into the gaps. This makes it possible to bring about improvement in heat exchangeability in the flow passage.
  • a plate-type heat exchanger is required to be configured such that positioning of the inner fin with relative to the heat transfer plates is performed during assembling at the time of manufacture.
  • Patent Literature 1 is unclear about a configuration in which positioning of the inner fin is performed.
  • the present invention has been made in view of the above circumstances and is aimed at providing a plate-type heat exchanger configured to allow positioning of an inner fin to be performed with improvement in in-plane distributive performance of a fluid, a heat pump device, and a heat-pump-type cooling and heating hot-water supply system.
  • a plate-type heat exchanger includes a plurality of heat transfer plates stacked on top of each other, a flow passage, formed by each space between the plurality of heat transfer plates, through which a fluid flows in a first direction, an inner fin disposed in the flow passage, a first projecting portion provided on an inflow side of each of the heat transfer plates and configured to prevent the fluid from flowing into gaps between both ends of the inner fin in a second direction and both ends of the heat transfer plate in the second direction, and a second projecting portion formed on an outflow side of each of the heat transfer plates and configured to perform positioning in placing the inner fin into the heat transfer plate.
  • the first direction is a direction of flow of the fluid through the flow passage.
  • the second direction is a direction orthogonal to the first direction.
  • the inner fin is disposed between the first projecting portion and the second projecting portion.
  • the first projection portion provided on an inflow side of each of the heat transfer plates and configured to prevent the fluid from flowing into gaps between both ends of the inner fin in the second direction and both ends of the heat transfer plate in the second direction makes it possible to improve the in-plane distributive performance of the fluid in the flow passage.
  • the second projecting portion formed on an outflow side of each of the heat transfer plates and configured to perform positioning in placing the inner fin into the heat transfer plate and the disposition of the inner fin between the first projecting portion and the second projecting portion make it possible to perform positioning of the inner fin.
  • plate-type heat exchangers according to embodiments of the present invention are described, for example, with reference to the drawings. Note that components given identical signs in the following diagrams including FIG. 1 are identical with or equivalent to each other and these signs are added to throughout the full text of the embodiments described below.
  • the terms showing directions are intended for illustrative purposes, and are not intended to limit the present invention.
  • the terms “upper”, “lower”, “right”, “left”, “front”, and “back” are used in a state where a plate-type heat exchanger 100 is viewed from the front; that is, the plate-type heat exchanger 100 is seen in a direction of stacking of heat transfer plates.
  • the terms “depressed” and “projecting” a portion that projects forward is deemed to be “projecting”, and a portion that projects backward is deemed to be “depressed”.
  • FIG. 1 is an exploded side perspective view of a plate-type heat exchanger according to Embodiment 1 of the present invention.
  • FIG. 2 is a front view of a first heat transfer plate of the plate-type heat exchanger according to Embodiment 1 of the present invention.
  • FIG. 3 is a front view of a second heat transfer plate of the plate-type heat exchanger according to Embodiment 1 of the present invention.
  • FIG. 4 is a front perspective view of a heat transfer set of the plate-type heat exchanger according to Embodiment 1 of the present invention.
  • FIG. 4 is a perspective view
  • FIG. 4 is a diagram that is substantially close to a front view.
  • FIG. 5 is a cross-sectional view taken along line A-Ain FIG. 4 .
  • FIG. 6 is an end elevation view of a cross-section taken along line B-B in FIG. 4 .
  • FIG. 7 is a cross-sectional view taken along line B-B in FIG. 4 .
  • FIG. 8 is an end elevation view of a cross-section taken along line C-C in FIG. 4 .
  • a plate-type heat exchanger 100 of Embodiment 1 is configured such that a first heat transfer plate and a second heat transfer plate are alternately stacked, and has a flow passage formed by a space between adjacent heat transfer plates.
  • An arrangement of flow passages in a direction of stacking constitutes alternation of a first flow passage 6 through which a first fluid flows and a second flow passage 7 through which a second fluid flows.
  • a heat transfer set 200 includes the inner fin 4, the first heat transfer plate 1, the inner fin 5, and the second heat transfer plate 2 being stacked starting from the front.
  • the first heat transfer plate 1, the second heat transfer plate 2, the inner fin 4, and the inner fin 5 are each formed in the shape of a long plate.
  • the plate-type heat exchanger 100 includes a plurality of the heat transfer sets 200 being stacked, and the first fluid flowing through the first flow passage 6 and the second fluid flowing through the second flow passage 7 exchange heat with each other. Points of contact between the heat transfer sets 200 thus stacked are joined by brazing, and the plate-type heat exchanger 100 is formed in a cuboidal shape as a whole.
  • the first fluid is water or brine, for example.
  • the second fluid is, for example, refrigerant such as R410A, R32, R290, or HFO mix or CO 2 .
  • the first fluid is indicated by a solid arrow
  • the second fluid is indicated by a dotted arrow.
  • a method by which the fluids flow indicates a counter-current flow configuration in which the first fluid and the second fluid flow in directions opposite to each other, the present invention is not limited to this flow method.
  • the method by which the fluids flow may be a co-current flow configuration in which the first fluid and the second fluid flow in an identical direction.
  • Operating pressure on the first fluid is the pressure of a pump that causes the first fluid to flow, and operations are always performed at low pressure. Further, operating pressure on the second fluid is the saturation pressure of the second fluid, and operations are always performed at high pressure.
  • first reinforcing side plate 3 and a second reinforcing side plate 8 are disposed on the outermost surfaces, respectively, of the heat transfer set 200 in the direction of stacking.
  • first reinforcing side plate 3 is a plate stacked on the foreground surface
  • second reinforcing side plate 8 is a plate stacked on the rearmost surface.
  • the first reinforcing side plate 3 and the second reinforcing side plate 8 are each formed in the shape of a long plate with its four corners rounded. In the four corners of the first reinforcing side pate 3, circular holes are formed. The circular holes serve as inflow ports or outflow ports through which a fluid flows in or flows out. Moreover, a cylindrically-shaped inflow pipe or outflow pipe is provided at a peripheral edge of each hole.
  • a first inflow pipe 9 through which the first fluid flows in is provided in the lower right corner of the first reinforcing side plate 3, and a first outflow pipe 10 through which the first fluid flows out is provided in the lower left corner of the first reinforcing side plate 3.
  • a second inflow pipe 11 through which the second fluid flows in is provided in the upper left corner of the first reinforcing side plate 3, and a second outflow pipe 12 through which the second fluid flows out is provided in the upper right corner of the first reinforcing side plate 3.
  • FIG. 1 shows a configuration in which the side plates are entirely uniform in wall thickness
  • the uniform configuration does not imply any limitation.
  • the wall thicknesses of portions of the side plates near the inflow pipes and the outflow pipes may be greater than the wall thicknesses of other portion, for example.
  • inflow pipes and the outflow pipes are identical in dimension, this does not imply any limitation, and the inflow pipes and the outflow pipes do not need to be identical in dimension.
  • the first heat transfer plate 1 and the second heat transfer plate 2 have holes that face the first inflow pipe 9, the first outflow pipe 10, the second inflow pipe 11, and the second outflow pipe 12, respectively.
  • the first heat transfer plate 1 is provided in the lower right corner thereof a first inflow hole 13 through which the first fluid flows in, and is provided in the lower left corner thereof a first outflow hole 14 through which the first fluid flows out.
  • the first heat transfer plate 1 is provided in the upper left corner thereof a second inflow hole 15 through which the second fluid flows in, and is provided in the upper right corner thereof a second outflow hole 16 through which the second fluid flows out. Moreover, the first heat transfer plate 1 has a cylindrically-shaped surrounding walls W 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 configured not to communicate with the first flow passage 6. This prevents the second fluid from flowing into the first flow passage 6 through the second inflow hole 15 and the second outflow hole 16.
  • the second heat transfer plate 2 is provided in the lower right corner thereof a first inflow hole 17 through which the first fluid flows in, and is provided in the lower left corner thereof a first outflow hole 18 through which the first fluid flows out.
  • the second heat transfer plate 2 is provided with, in the upper left corner thereof, a second inflow hole 19 through which the second fluid flows in, and is provided with, in the upper right corner thereof, a second outflow hole 20 through which the second fluid flows out.
  • the second heat transfer plate 2 has cylindrically-shaped surrounding walls W 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 configured not to communicate with the second flow passage 7. This prevents the first fluid from flowing into the second flow passage 7 through the first inflow hole 17 and the first outflow hole 18.
  • the first heat transfer plate 1 and the second heat transfer plate 2 are hereinafter referred to collectively as “heat transfer plates” when it is not necessary to distinguish between them.
  • the first reinforcing side plate 3 and the second reinforcing side plate 8 are hereinafter referred to collectively as “side plates” when it is not necessary to distinguish between them.
  • the first flow passage 6 and the second flow passage 7 are hereinafter referred to collectively as “flow passages” when it is not necessary to distinguish between them.
  • first direction refers to a direction of flow of a fluid, that is, a horizontal direction of FIG. 1
  • second direction refers to a direction orthogonal to the first direction, that is, a vertical direction of FIG. 1 .
  • each of the heat transfer plates has a flat portion 30 and outer wall portions 31 extending outward from both ends of the flat portion 30 in the second direction, and the outer wall portions 31 of heat transfer plates that are adjacent to each other in the direction of stacking are in contact with each other. Moreover, a space is formed between each flat portion 30 and an adjacent flat portion 30, and this space serves as the first flow passage 6 or the second flow passage 7. In FIG. 5 , the first flow passage 6 is located above the first heat transfer plate 1, and the second flow passage 7 is located between the first heat transfer plate 1 and the second heat transfer plate 2. Further, as shown in FIGS. 2 and 3 , each of the heat transfer plates has header portions 24 provided at both ends thereof in the first direction.
  • each of the heat transfer plates may be made of a material such as stainless steel, carbon steel, aluminum, copper, or an alloy thereof, the following description assumes that each of the heat transfer plates is made of stainless steel.
  • the inner fin 4 has a height 11 (see FIG. 5 ) that is equal to a flow passage height of the first flow passage 6, and is in contact with the flat portion 30 of the first heat transfer plate 1 and the flat portion 30 of the second heat transfer plate 2. The points of contact may be joined, for example, by brazing or may not be joined.
  • the inner fin 5 has a height 12 (see FIG. 5 ) that is equal to a flow passage height of the second flow passage 7, and is in contact with the flat portion 30 of the first heat transfer plate 1 and the flat portion 30 of the second heat transfer plate 2.
  • the height l1 of the inner fin 4 is greater than the height 12 of the inner fin 5, in this example, those heights may be equal to each other, or this relationship may be inverted.
  • the inner fins used in this example are offset fins.
  • the offset fins are configured such that corrugated portions each formed in a corrugated shape by alternately coupling, in the second direction, vertical walls 32 oriented perpendicularly to the heat transfer plate and horizontal walls 33 oriented parallel to the heat transfer plate are formed in a staggered arrangement in the first direction with half-wave shifts.
  • the inner fins are not limited to offset fins and may be of any one of a flat-plate fin type, a corrugated fin type, a louver type, a wavy fin, a corrugated fin type, and a pin fin type, or two or more of these types may be combined.
  • gaps 21 are formed between both ends of the inner fin 4 in the second direction and both ends of the first heat transfer plate 1 in the second direction or, specifically, the outer wall portions 31.
  • the first fluid having flowed into the first flow passage 6 through the first inflow hole 13 of the first heat transfer plate 1 easily flows into the gaps 21, as the first fluid is subjected to a weaker resistance than in a case where it flows into the inner fin 4. For this reason, the first fluid preferentially flows into the gaps 21 without uniformly flowing through the first flow passage 6. This deteriorates heat exchange performance.
  • the first heat transfer plate 1 has first projecting portions 22 provided upstream of the gaps 21.
  • the first projecting portions 22 are provided upstream of an edge of the inner fin 4 through which the fluid flows in and at both ends of the first heat transfer plate 1 in the second direction.
  • the first projecting portions 22 are formed by projecting portions projecting from the flat portion 30 of the first heat transfer plate 1 toward the first flow passage 6, and are formed by press working. The first projecting portions 22 prevent the first fluid from flowing into the gaps 21.
  • the first heat transfer plate 1 has a second projecting portion 23 provided downstream of an edge of the inner fin 4 through which the fluid flows out.
  • the second projecting portion 23 is provided in a location at a length of the first heat transfer plate 1 in the first direction from the first projecting portions 22.
  • the second projecting portion 23 includes a projecting portion projecting from the flat portion 30 of the first heat transfer plate 1 toward the first flow passage 6, and is formed by press working.
  • the second projecting portion 23 may be located off the central part of the first heat transfer plate 1 in the second direction as shown in FIG. 2 or may be located in the central part, and is not limited to any particular location in the second direction.
  • the locations of both ends of the inner fin 4 in the first direction are determined, so that the inner fin 4 can be positioned in the first direction in being placed onto the first heat transfer plate 1.
  • the first projecting portions 22 and the second projecting portion 23 are each formed in a circular shape.
  • the first projecting portions 22 and the second projecting portion 23 are limited to a circular shape.
  • the first projecting portions 22 and the second projecting portion 23 may each be formed in any one of shapes such as a triangle, a quadrangle, and an ellipse, or two or more of these shapes may be combined.
  • gaps 25 are similarly formed between both ends of the inner fin 5 in the second direction and both ends of the second heat transfer plate 2 in the second direction or, specifically, the outer wall portions 31.
  • the second fluid having flowed into the second flow passage 7 through the second inflow hole 19 of the second heat transfer plate 2 easily flows into the gaps 25, as the second fluid is subjected to a weaker resistance than in a case where it flows into the inner fin 5. For this reason, the second fluid preferentially flows into the gaps 25 without uniformly flowing through the second flow passage 7. This causes a decrease in heat exchange performance.
  • the second heat transfer plate 2 has first projecting portions 26 provided upstream of the gaps 25.
  • the first projecting portions 26 are provided upstream of an edge of the inner fin 5 through which the fluid flows in and at both ends of the second heat transfer plate 2 in the second direction.
  • the second projecting portions 26 include projecting portions projecting from the flat portion 30 of the second heat transfer plate 2 toward the second flow passage 7, and are formed by press working. The first projecting portions 26 prevent the second fluid from flowing into the gaps 25.
  • the second heat transfer plate 2 has a second projecting portion 27 provided downstream of an edge of the inner fin 5 through which the fluid flows out.
  • the second projecting portion 27 is provided in a location at a length of the second heat transfer plate 2 in the first direction from the first projecting portions 26.
  • the second projecting portion 27 is formed by a projecting portion projecting from the flat portion 30 of the second heat transfer plate 2 toward the second flow passage 7, and is formed by press working.
  • the second projecting portion 27 may be located off the central part of the second heat transfer plate 2 in the second direction as shown in FIG. 3 or may be located in the central part, and is not limited to any particular location in the second direction.
  • the locations of both ends of the inner fin 5 in the first direction are determined, so that the inner fin 5 can be positioned in the first direction in being placed onto the second heat transfer plate 2.
  • the first projecting portions 26 and the second projecting portion 27 are each formed in a circular shape.
  • the first projecting portions 26 and the second projecting portion 27 are not limited to being circular in shape.
  • the first projecting portions 26 and the second projecting portion 27 may each be formed in any one of shapes such as a triangle, a quadrangle, and an ellipse, or two or more of these shapes may be combined.
  • the inner fin 4 has a shape of asperities in fine cycles. Spacings between two vertical walls 32 of the inner fin 4 that are adjacent to each other in the second direction are the same across the second direction. Moreover, in order that positioning of the inner fin 4 can be performed with an end of the inner fin 4 in the first direction surely in contact with the first projecting portions 22, it is desirable that as shown in FIG. 7 , the width ⁇ of each of the first projecting portions 22 be twice or more as great as the distance ⁇ between two adjacent vertical walls 32 of the inner fin 4. Making the width ⁇ of each of the first projecting portions 22 twice or more as great as the distance ⁇ between the two vertical walls 32 means that the width ⁇ of each of the first projecting portions 22 is greater than or equal to one cycle of asperities of the inner fin 4.
  • the inner fin 4 is designed to get the most out of the width of the flat portion 30 of the heat transfer plate in the second direction. Therefore, the difference between the width of the inner fin 4 in the second direction and the width of the flat portion 30 in the second direction is shorter than one cycle of asperities of the inner fin 4. Therefore, by making the width ⁇ of each of the first projecting portions 22 twice or more as great as the distance ⁇ between the two vertical walls 32, positioning of the inner fin 4 can be performed with the end of the inner fin 4 in the first direction surely in contact with the first projecting portions 22.
  • an increase in the width ⁇ of each of the first projecting portions 22 leads to an increase in ease of positioning of the inner fin 4 but results in the formation of a portion in the inner fin 4 into which the fluid hardly flows.
  • a simple corrugated plate that is, a fin configured such that a fluid flows only in one direction may result in the formation of a corrugated portion where insufficient inflow occurs.
  • a fin such as an offset fin, configured such that a fluid both flows in a mainstream direction (indicated by an arrow in FIG. 2 ) and moderately flows in a direction of flow that intersects the mainstream direction.
  • the width ⁇ of each of the first projecting portions 22 be five times or less as great as the distance ⁇ between two adjacent vertical walls 32 of the inner fin 4.
  • each of the first projecting portions 22 is made five times or less as great as the distance ⁇ between two adjacent vertical walls 32 of the inner fin 4.
  • the width ⁇ of each of the first projecting portions 22 is made five times or less as great as the distance ⁇ , as flow through a fin portion is affected when the width ⁇ is more than five times as great as the distance ⁇ .
  • the width ⁇ of each of the first projecting portions 26 is twice or more and five times or less as great as the distance ⁇ between two adjacent vertical walls 32 of the inner fin 5.
  • the width ⁇ of each of the second projecting portions 23 and 27 be twice or more and five times or less as great as the distance ⁇ between two adjacent vertical walls 32 of the inner fin.
  • These points of contact may be joined, for example, by brazing or may not be joined.
  • Each first projecting portion 22 is provided within an area surrounded by a first line ⁇ representing an inflow edge of both edges of the inner fin 4 in the first direction, two second lines ⁇ representing both edges of the flat portion 30 in the second direction, and two circular arcs 28 indicated by dotted lines in FIG. 4 .
  • Each of the circular arcs 28 is a circular arc with a radius R centered at a point of intersection O of the first line ⁇ and a corresponding one of the second lines ⁇ , and the radius R is three times as great as the flow passage height l1 of the first flow passage 6.
  • the gaps 21 between the inner fin 4 and the outer wall portions 31 each measure approximately 1 mm.
  • the height l1 of the inner fin 4 is approximately 0.5 mm to 2.5 mm.
  • a "triple" of the height l1 of the inner fin 4 ranges from 1.5 mm to 7.5 mm.
  • the distance between two adjacent vertical walls 32 of the inner fin 4 is approximately 0.5 mm to 1.5 mm.
  • the width ⁇ of each of the first projecting portions 22 is approximately 1.0 mm to 7.5 mm, as it is desirable that the width ⁇ of each of the first projecting portions 22 be twice or more and five times or less as great as the distance between two adjacent vertical walls 32 of the inner fin 4. Therefore, for minimization of the gaps 21 between the inner fin 4 and the outer wall portions 31 and enhancement of the effect of inhibiting the flow rate of the first fluid that flows into the gaps 21, the radius R is made three times as great as the flow passage height 11 of the first flow passage 6.
  • each first projecting portion 26 is provided within an area surrounded by a first line representing an inflow edge of both edges of the inner fin 5 in the first direction, two second lines representing both edges of the flat portion 30 in the second direction, and two circular arcs.
  • Each of the circular arcs is a circular arc with a radius R centered at a point of intersection of the first line and a corresponding one of the second lines, and the radius R is three times as great as the flow passage height 12 of the second flow passage 7.
  • the first fluid having flowed into the first flow passage 6 flows through the inner fin 4 in a direction from right to left as indicated by a solid arrow in FIG. 2 while gradually spreading toward the outer wall portions 31 of the first heat transfer plate 1 and flows out from the first outflow pipe 10 via the first outflow hole 14 of the first heat transfer plate 1.
  • the second fluid having flowed into the second inflow pipe 11 from outside flows into the second flow passage 7 via the second inflow hole 19 of the second heat transfer plate 2.
  • the second fluid having flowed into the second flow passage 7 flows through the inner fin 5 in a direction from left to right as indicated by a dotted arrow in FIG. 3 while spreading toward the outer wall portions 31 of the second heat transfer plate 2 and flows out from the second outflow pipe 12 via the second outflow hole 20 of the second heat transfer plate 2.
  • the flow of the first fluid through the first flow passage 6 and the flow of the second fluid through the second flow passage 7 allow the first fluid and the second fluid to exchange heat with each other via the first heat transfer plate 1 and the second heat transfer plate 2.
  • first projecting portions 22 in the first flow passage 6 prevents the first fluid of the first flow passage 6 from flowing into the gaps 21. This makes it possible to rectify an imbalance of the first fluid in the first flow passage 6 and bring about improvement in distributive performance to both the upper and lower sides of FIG. 2 .
  • imbalances of the fluids can be better rectified than in a case where they are not provided. This can result in improvement in performance of the plate-type heat exchanger 100.
  • the first projecting portions 22 are provided on an inflow side of the first heat transfer plate 1. This makes it possible to inhibit the first fluid from preferentially flowing into the gaps 21 and improve the in-plane distributive performance of the first fluid in the first flow passage 6. Further, the second projecting portion 23, which performs positioning in placing the inner fin 4 into the first flow passage 6, is provided on an outflow side of the first heat transfer plate 1.
  • the positioning of the inner fin 4 or the inner fin 5 can be achieved by the first projecting portions and the second projecting portion.
  • This makes it possible to increase the distance between the inner fin and another projecting and depressed structure configured to improve strength, and makes it possible to design a projecting and depressed structure distribution that is compatible with both distributiveness and strength performance. This can result in achieving an increase in performance of the plate-type heat exchanger 100.
  • the inner fin includes an offset fin having a corrugated portion formed in a corrugated shape by alternately coupling, in the second direction, vertical walls 32 oriented perpendicularly to the heat transfer plate and horizontal walls 33 oriented parallel to the heat transfer plate.
  • the width of each of the first projecting portions in the second direction is twice or more as great as the distance between two adjacent vertical walls 32 of the inner fin.
  • the width of each of the first projecting portions in the second direction is five times or less as great as the distance between two adjacent vertical walls 32 of the inner fin. This makes it possible to reduce an area of insufficient inflow of the fluid into the inner fin.
  • the width of the second projecting portion may be twice or more and five times or less as great as the distance between two adjacent vertical walls 32 of the inner fin.
  • the first projecting portions and the second projecting portion may be provided to project toward the flow passage from one of the two heat transfer plates forming the flow passage. Moreover, improvement in strength can be brought about by configuring the first projecting portions and the second projecting portion to be joined to the other one of the two heat transfer plates forming the flow passage.
  • first projecting portions which are provided on the inflow sides of the heat transfer plates
  • second projecting portions which are provided on the outflow sides of the heat transfer plates
  • the first projecting portions 22 of the first flow passage 6 and the second projecting portion 27 of the second flow passage 7 are identical in shape to each other, and are in contact with each other with an overlap in location in the second direction in a cross-section perpendicular to the direction of stacking. Further, the second projecting portion 23 of the first flow passage 6 and the first projecting portions 26 of the second flow passage 7 are identical in shape to each other, and are in contact with each other with an overlap in location in the second direction in a cross-section perpendicular to the direction of stacking. This makes it possible to improve the strength of the plate-type heat exchanger 100.
  • the first projecting portions are provided at both ends of the flat portion 30 of the heat transfer plate in the second direction and within an area surrounded by a first line representing an inflow edge of both edges of the inner fin in the first direction, two second lines representing both edges of the flat portion in the second direction, and two circular arcs at both ends of the flat portion in the second direction.
  • Each of the two circular arcs is a circular arc with a radius R centered at a point of intersection of the first line and a corresponding one of the second lines, and the radius R is three times as great as the flow passage height of the flow passage. This makes it possible to enhance the effect of inhibiting the fluid from flowing into the gaps.
  • the second projecting portions are provided at both ends of the flat portion in the second direction and within an area surrounded by a third line representing an outflow edge of both edges of the inner fin in the first direction, two second lines, and two circular arcs at both ends of the flat portion in the second direction.
  • Each of the two circular arcs is a circular arc with a radius R centered at a point of intersection of the third line and a corresponding one of the second lines, and the radius R is three times as great as the flow passage height of the flow passage. This makes it possible to enhance the effect of inhibiting the fluid from flowing into the gaps.
  • Embodiment 1 the second projecting portion 23 and the second projecting portion 27 are each formed in one place.
  • second projecting portions 23 are formed in two places, and second projecting portions 27 are formed in two places.
  • the following mainly describes points in which Embodiment 2 differs from Embodiment 1, and omits to describe constituent elements of Embodiment 2 that are similar to those of Embodiment 1.
  • FIG. 9 is a front perspective view of a heat transfer set of a plate-type heat exchanger according to Embodiment 2 of the present invention.
  • FIG. 10 is an end elevation view of a cross-section taken along line B-B in FIG. 9 .
  • FIG. 11 is an end elevation view of a cross-section taken along line C-C in FIG. 9 .
  • Embodiment 2 is identical to Embodiment 1 except for the numbers and locations of second projecting portions 23 and second projecting portions 27.
  • the first heat transfer plate 1 of the heat transfer set 200 of Embodiment 2 has second projecting portions 23 provided in locations at a length of the inner fin 4 in the first direction from the first projecting portions 22 and at both ends of the first heat transfer plate 1 in the second direction.
  • the second heat transfer plate 2 has second projecting portions 27 provided in locations at a length of the inner fin 4 in the first direction from the first projecting portions 26 and, as shown in FIG. 10 , at both ends of the second heat transfer plate 2 in the second direction.
  • Embodiment 2 brings about the same effects as Embodiment 1 and, in addition, brings about the following effects. That is, while Embodiment 1 has one second projecting portion 23 and one second projecting portion 27, Embodiment 2 has two second projecting portions 23 provided at both ends of a heat transfer plate in the second direction and two second projecting portions 27 provided at both ends of a heat transfer plate in the second direction.
  • the second projecting portions 23 are located on an outflow side of the first flow passage 6, and the second projecting portions 27 are located on an outflow side of the second flow passage 7. Therefore, in the first flow passage 6, outflow sides of the gaps 21, which extend in a horizontal direction, are closed by the second projecting portions 23, and in the second flow passage 7, outflow sides of the gaps 25, which extend in a horizontal direction in FIG. 9 , are closed by the second projecting portions 27.
  • Embodiment 2 can bring about further improvement in in-plane distributive performance than Embodiment 1. This makes it possible to achieve an increase in performance of the plate-type heat exchanger 100.
  • each second projecting portion 23 is provided within an area surrounded by a third line ⁇ representing an outflow edge of both edges of the inner fin 4 in the first direction, two second lines ⁇ , and two circular arcs 28.
  • Each of the circular arcs 28 is a circular arc with a radius R centered at a point of intersection O of the third line ⁇ and a corresponding one of the second lines ⁇ , and the radius R is three times as large as the flow passage height l1 of the first flow passage 6.
  • each second projecting portion 27 is provided within an area surrounded by a third line representing an outflow edge of both edges of the inner fin 5 in the first direction, two second lines ⁇ , and two circular arcs.
  • Each of the circular arcs is a circular arc with a radius R centered at a point of intersection O of the third line and a corresponding one of the second lines ⁇ , and the radius R is three times as large as the flow passage height 12 of the second flow passage 7.
  • FIG. 12 is a cross-sectional view taken along line A-A in a case where heat transfer plates according to a modification are used in the plate-type heat exchanger of FIG. 9 .
  • FIG. 13 is a cross-sectional view taken along line B-B in a case where the heat transfer plates according to the modification are used in the plate-type heat exchanger of FIG. 9 .
  • FIG. 14 is a cross-sectional view taken along line C-C in a case where the heat transfer plates according to the modification are used in the plate-type heat exchanger of FIG. 9 .
  • the first heat transfer plate 1 and the second heat transfer plate 2 of the modification shown in FIGS. 12 and 13 each include two plates partially joined to each other.
  • the first heat transfer plate 1 includes plates 1a and 1b partially joined to each other.
  • the second heat transfer plate 2 includes plates 2a and 2b partially joined to each other.
  • black portions 29 between plates indicate junctions.
  • a heat transfer plate thus including two plates partially joined to each other, a micro-flow passage communicating with outside air is formed between the two plates. For this reason, even if a defect in a heat transfer plate dividing adjacent flow passages of two types of fluid causes leakage of a fluid into a flow passage, mixture of the two types of fluid between the flow passages (leakage into a room) can be avoided by surely draining the leaked fluid out of the flow passage. This makes it possible to use flammable refrigerant as a fluid that flows through a flow passage.
  • the heat transfer plates of the modification shown in FIGS. 12 to 14 are applicable not only to Embodiment 2 but also to Embodiment 1 and Embodiment 3, which is described below.
  • Embodiment 3 differs from Embodiment 2, and omits to describe components of Embodiment 3 that are similar to those of Embodiment 2.
  • FIG. 15 is a front perspective view of a heat transfer set of a plate-type heat exchanger according to Embodiment 3 of the present invention.
  • FIG. 15 is a diagram that is substantially close to a front view.
  • FIG. 16 is a front view of a first heat transfer plate of FIG. 15 .
  • FIG. 17 is a cross-sectional view taken along line A-A in FIG. 15 .
  • FIG. 18 is an end elevation view of a cross-section taken along line B-B in FIG. 15 .
  • FIG. 19 is an end elevation view of a cross-section taken along line C-C in FIG. 15 .
  • the opposite of Embodiment 2 is true in FIG. 15 ; that is, the second heat transfer plate 2 is situated at the front, and the first heat transfer plate 1 is situated at the back.
  • the second heat transfer plate 2 has circular first projecting portions 26 provided on an inflow side thereof and circular second projecting portions 27 provided on an outflow side thereof.
  • the first projecting portions 26 and the second projecting portions 27 are in contact with the first heat transfer plate 1, and these points of contact are joined, for example, by brazing.
  • the first projecting portions 26 and the second projecting portions 27 are equal in height to the inner fin 5.
  • the second heat transfer plate 2 of Embodiment 3 further has circular arc first depressed portions 40 formed to surround inflow sides of the first projecting portions 26.
  • the second heat transfer plate 2 of Embodiment 3 further has circular arc second depressed portions 41 formed to surround outflow sides of the second projecting portions 27.
  • the first depressed portions 40 and the second depressed portions 41 include depressed portions depressed from the second heat transfer plate 2 toward the first flow passage 6.
  • the first depressed portions 40 and the second depressed portions 41 are half as high as the inner fin 4.
  • the first heat transfer plate 1 has circular arc first projecting portions 22a and circular arc second projecting portions 23a formed instead of the circular first projecting portions 22 and the circular second projecting portions 23 of Embodiment 2.
  • the first projecting portions 22a and the second projecting portions 23a include projecting portions projecting from the first heat transfer plate 1 toward the first flow passage 6.
  • the projecting portions 22a and the second projecting portions 23a are half as high as the inner fin 4.
  • the first projecting portions 22a and the second projecting portions 23a are in contact with the second depressed portions 41 and the first depressed portions 40, respectively, of the second heat transfer plate 2, and these points of contact are joined, for example, by brazing.
  • the circular arc projecting portions formed on the first heat transfer plate 1 and the circular projecting portions formed on the second heat transfer plate 2 are different in shape from each other.
  • Such a configuration of the first heat transfer plate 1 and the second heat transfer plate 2 causes circular arc flow passage blocking portions to be formed by contact between the second depressed portions 41 and the first projecting portions 22a upstream of the gaps 21 in the first flow passage 6, so that the inflow of the first fluid into the gaps 21 can be inhibited.
  • circular arc flow passage blocking portions are formed by contact between the first depressed portions 40 and the second projecting portions 23a downstream of the gaps 21. That is, the flow passage blocking portions are formed both upstream and downstream of the gaps 21.
  • the first projecting portions 26 and the second projecting portions 27 are provided upstream and downstream, respectively, of the gaps 25 in the second flow passage 7. This makes it possible to inhibit the second fluid from flowing into the gaps 25.
  • Embodiment 3 has illustrated a configuration in which the circular arc first projecting portions 22a and the circular arc second projecting portions 23a are formed on the first heat transfer plate 1 and the circular projecting portions 26, the circular second depressed portions, the circular arc first depressed portions 40, and the circular arc second depressed portions 41 are formed on the second heat transfer plate 2, the opposite may be true.
  • the first projecting portions 22a and the second projecting portion 23a are not limited to being circular arc in shape.
  • the first projecting portions 22a and the second projecting portion 23a may each be formed in any one of other shapes such as a triangle, a quadrangle, and an ellipse, or two or more of these shapes may be combined.
  • Embodiment 3 brings about the same effects as Embodiment 2 and brings about the following effects. That is, the structure in which the first heat transfer plate 1 and the second heat transfer plate 2 are joined at the flat portions 30 by a combination of projecting portions and depressed portions brings about improvement in strength. Further, since the first projecting portion 22a and the second projecting portions 23a of the first flow passage 6 are half as high as the first flow passage 6, the combination of projecting portions and depressed portions can be applied to a wider range due to manufacturing restrictions on percentages of elongation of the heat transfer plates.
  • the first flow passage 6 composed of projecting portions of Embodiment 3 can be made twice as high as the first flow passage 6 composed of projecting portions of Embodiment 1. This makes it possible to easily achieve optimization of the height of the first flow passage 6 composed of projecting portions of Embodiment 3. Alternatively, this makes it possible to more easily achieve optimization of the size of the first projecting portions 22a and the second projecting portions 23a and the height of the first flow passage 6, thus making it possible to achieve an increase in performance of the plate-type heat exchanger 100.
  • the first projecting portions 22a of the first heat transfer plate 1 and the second projecting portions 27 of the second heat transfer plate 2 are different in shape from each other, and are different in location in the second direction in a cross-section perpendicular to the direction of stacking.
  • the second projecting portions 23a of the first heat transfer plate 1 and the first projecting portions 26 of the second heat transfer plate 2 are different in shape from each other, and are different in location in the second direction in a cross-section perpendicular to the direction of stacking.
  • the combination of projecting portions and depressed portions makes it possible to inhibit the inflow of the fluids into the gaps.
  • Embodiment 4 is intended to bring about improvement in strength by providing the header portions 24 with projecting and depressed structures. The following mainly describes points in which Embodiment 4 differs from Embodiment 1, and omits to describe components of Embodiment 4 that are similar to those of Embodiment 1.
  • FIG. 20 is a partial front perspective view of a heat transfer set of a plate-type heat exchanger according to Embodiment 4 of the present invention.
  • FIG. 21 is a cross-sectional view taken along line D-D in FIG. 20 .
  • the header portions 24 provided on the inflow and outflow sides, respectively, of the first heat transfer plate 1 are provided with a plurality of depressed portions 50 dispersed. Further, the header portions 24 provided on the inflow and outflow sides, respectively, of the second heat transfer plate 2 are provided with a plurality of depressed portions 51 facing the depressed portions 50.
  • Top faces of the projecting portions 51 are in contact with bottom faces of the depressed portions 50, and these points of contact are joined.
  • the depressed portions 50 and the projecting portions 51 are formed in circular shapes and configured to be equal in diameter and height to each other.
  • the depressed portions 50 are not provided in an area in the outflow-side header portion 24 extending over a distance ⁇ from the third line ⁇ of the inner fin 4. Similarly, the depressed portions 50 are not provided in an area in the inflow-side header portion 24 extending over the distance ⁇ from the first line ⁇ of the inner fin 4.
  • the projecting portions 51 are not provided in an area in the outflow-side header portion 24 extending over the distance ⁇ from the third line ⁇ of the inner fin 5, although not illustrated.
  • the depressed portions 50 are not provided in an area in the inflow-side header portion 24 extending over the distance ⁇ from the first line ⁇ of the inner fin 5.
  • the distance ⁇ be equal to or greater than an equivalent diameter of a cross-sectional shape E obtained by cutting a junction between a depressed portion 50 and a projecting portion 51 along a surface perpendicular to the first direction through the center of the junction: ⁇ ⁇ 2 w 1 / w + 1 , where w is the diameter of the depressed portion 50 and the projecting portion 51 and 1 is the height of the junction between the depressed portion 50 and the projecting portion 51.
  • FIG. 22 is a diagram showing a flow velocity distribution of a fluid in an inner fin according to a comparative example provided with a projecting and depressed structure in the area extending over the distance ⁇ from the first line ⁇ .
  • FIG. 22 is equivalent to a velocity distribution in a cross-sectional taken along line F-F in FIG. 23 below.
  • the horizontal axis represents the second direction of the inner fin
  • the vertical axis represents the flow velocity.
  • FIG. 23 is a diagram showing a velocity distribution of inflow into the inner fin according to the comparative example provided with the projecting and depressed structure in the area extending over the distance ⁇ from the first line ⁇ .
  • FIG. 23 a longer arrow indicates a higher flow velocity.
  • FIG. 24 is a diagram showing a velocity distribution of inflow into the inner fin of the plate-type heat exchanger according to Embodiment 4 of the present invention in a case where no projecting and depressed structure is provided in the area extending over the distance ⁇ from the first line ⁇ .
  • the horizontal axis X represents the second direction of the inner fin
  • the vertical axis Y represents the first direction of the inner fin
  • the arrows indicate the magnitude of the flow velocity.
  • Embodiment 4 which is configured such that no projecting and depressed structure 52 is provided in the area extending over the distance ⁇ from the first line ⁇ , ensures uniformity of flow velocity across the inner fin 5 in the second direction.
  • FIGS. 22 to 24 are diagrams for making a comparison between a case where a projecting and depressed structure 52 is provided in the area extending over the distance ⁇ from the first line ⁇ and a case where no projecting and depressed structure 52 is provided in the area extending over the distance ⁇ from the first line ⁇ , and the first projecting portions 26, which serve to inhibit the inflow of the second fluid into the gaps 25 at both ends of the second flow passage 7, are not provided. For this reason, the flow velocity is high at both ends of the inner fin 5 in the second direction.
  • FIG. 25 shows a flow velocity distribution in a case where the first projecting portions 26 are provided.
  • FIG. 25 is a diagram showing a velocity distribution of inflow into an inner fin in a configuration having first projecting portions in addition to a projecting and depressed structure.
  • the horizontal axis X represents the second direction of the inner fin
  • the vertical axis Y represents the first direction of the inner fin
  • the arrows indicate the magnitude of the flow velocity.
  • FIG. 25 which is a diagram for explaining the effect of the first projecting portions, shows a case where a projecting and depressed structure 52 is provided in the area extending over the distance ⁇ from the first line ⁇ .
  • the provision of the first projecting portions 26 makes the flow velocity in the gaps at both ends of the second flow passage 7 lower than it is in FIG. 24 .
  • Embodiment 4 brings about the same effects as Embodiment 1 by providing the first projecting portions and can bring about improvement in strength of the header portions 24 by providing the header portions 24 with the projecting and depressed structures 52.
  • Embodiment 4 is configured such that the projecting and depressed structures 52 are not provided at least in the areas extending over the distance ⁇ from the first line ⁇ and the third line ⁇ , respectively. This makes it possible to rectify a problem of a decrease in in-plane distributive performance caused by providing the header portions 24 with the projecting and depressed structures 52 and ensure uniformity of flow velocity of the fluid across the inner fin in the second direction.
  • Embodiments 1 to 4 features of the embodiments may be combined as appropriate to constitute a plate-type heat exchanger 100.
  • Embodiment 1 and Embodiment 3 may be combined such that the width of each of the first and second projecting portions 26 and 27 in Embodiment 3 is twice or more and five times or less as great as the distance between two adjacent vertical walls of the inner fin.
  • Embodiment 3 and Embodiment 4 may be combined to be configured such that the header portions 24 of the heat transfer set 200 of Embodiment 3 shown in FIG. 15 are provided with the projecting and depressed structures 52 of Embodiment 4.
  • a modification that is applied to the same constituent element of each of Embodiments 1 to 4 is similarly applied to an embodiment other than the embodiment in which the modification is described.
  • Embodiment 5 illustrates a heat pump device mounted with the plate-type heat exchanger 100 described in Embodiments 1 to 4.
  • the following describes a heat-pump-type cooling and heating hot-water supply system as an example of a form of utilization of the heat pump device.
  • FIG. 26 is a schematic view showing a configuration of a heat-pump-type cooling and heating hot-water supply system according to Embodiment 5 of the present invention.
  • a heat-pump-type cooling and heating hot-water supply system 300 includes a heat pump device 65 and a heat medium circuit 70, and the heat pump device 65 includes a refrigerant circuit 60.
  • the refrigerant circuit 60 includes a compressor 61, a heat exchanger 62, a decompression device 63, and a heat exchanger being connected in sequence by pipes, and the decompression device 63 is formed of, for example, by an expansion valve or a capillary tube.
  • the heat medium circuit 70 includes the heat exchanger 62, a cooling and heating hot-water supply device 71, and a pump 72 being connected in sequence by pipes, and the pump 72 circulates a heat medium.
  • the compressor 61, the heat exchanger 62, the decompression device 63, and the heat exchanger 64 are housed in a housing of the heat pump device 65.
  • the heat exchanger 62 is the plate-type heat exchanger 100 described above in Embodiments 1 to 4, and carries out a heat exchange between refrigerant flowing through the refrigerant circuit 60 and the heat medium flowing through the heat medium circuit 70.
  • the heat medium that is used in the heat medium circuit 70 may be a fluid, such as water, ethylene glycol, propylene glycol, or a mixture thereof, that is capable of exchanging heat with the refrigerant of the refrigerant circuit 60.
  • the refrigerant flowing through the refrigerant circuit 60 is not limited to a particular refrigerant, and usable examples of the refrigerant include R22, R410A, or other refrigerants. Further, since the heat-pump-type cooling and heating hot-water supply system 300 allows no refrigerant to be supplied to an indoor side, flammable refrigerant such as R32, R290, or HFO mix may be used as the refrigerant.
  • the plate-type heat exchanger 100 which includes the heat exchanger 62, is incorporated into the heat-pump-type cooling and heating hot-water supply system 300 so that the refrigerant flows through the second flow passage 7, which is higher in heat-transfer performance than the first flow passage 6, and the heat medium flows through the first flow passage 6. Since the inner fin 4 and the inner fin 5 are equal in heat-transfer area to each other and the inner fin 5 is smaller in hydraulic diameter than the inner fin 4, the second flow passage 7 is higher in heat-transfer performance than the first flow passage 6.
  • the cooling and heating hot-water supply device 71 includes, for example, a hot water storage tank (not illustrated) or an indoor heat exchanger of an indoor unit (not illustrated) configured to perform indoor air conditioning.
  • the heat medium is water.
  • the water is heated by the heat exchanger 62 exchanging heat with the refrigerant of the refrigerant circuit 60.
  • the water thus heated is stored in the hot water storage tank (not illustrated).
  • cooling and heating hot-water supply device 71 is an indoor heat exchanger
  • indoor cooling or heating is performed by guiding the heat medium of the heat medium circuit 70 to the indoor heat exchanger and exchanging heat with indoor air.
  • the cooling and heating hot-water supply device 71 is not limited to a particular configuration such as that described above, and needs only be configured to be able to perform cooling and heating and hot-water supply through the use of heating energy of the heat medium of the heat medium circuit 70.
  • the heat exchanger 62 is used as a condenser, and in the case of cooling, the heat exchanger 62 is used as an evaporator.
  • Arrows shown in FIG. 26 indicate directions of flow of the refrigerant in the case of heating and hot-water supply, and in the case of cooling, the refrigerant flows in opposite directions (not illustrated).
  • the refrigerant flows into the second flow passage 7 of the heat exchanger 62 in the form of a two-phase gas-liquid flow. In so doing, the two-phase gas-liquid flow is prevented by the first projecting portions 22 from flowing into the gaps 21.
  • Embodiment 5 makes it possible to achieve an increase in performance and a reduction in cost by including the plate-type heat exchanger 100 of Embodiments 1 to 4. Further, Embodiment 5 makes it possible to obtain a heat-pump-type cooling and heating hot-water supply system 300 with high heat exchange efficiency. Further, Embodiment 5 makes it possible to obtain a highly-reliable heat-pump-type cooling and heating hot-water supply system 300 with improvement in strength. That is, Embodiment 5 makes it possible to achieve a heat-pump-type cooling and heating hot-water supply system 300 configured to have high heat exchange efficiency, consume less electric power, offer improved safety, and emit less CO 2 .
  • Embodiment 5 has described, as an example of application of the plate-type heat exchanger 100 described in the foregoing embodiments, a heat-pump-type cooling and heating hot-water supply system 300 configured to cause refrigerant and water to exchange heat with each other.
  • the plate-type heat exchanger 100 described in the foregoing embodiments is applicable not only to the plate-type heat exchanger 100 described in the foregoing embodiments but also to many industrial equipment and home appliances such as cooling chillers, generating equipment, and food heat sterilization equipment.
  • the plate-type heat exchanger 100 described in the foregoing embodiments is easy to manufacture, has improved heat exchange performance, and is applicable to a heat pump device whose energy saving performance needs to be improved.

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  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
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EP18940018.7A 2018-11-16 2018-11-16 Plattenwärmetauscher, wärmepumpenvorrichtung und kühlendes/erhitzendes heisswasserzufuhrsystem vom wärmepumpentyp Active EP3882556B1 (de)

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PCT/JP2018/042436 WO2020100276A1 (ja) 2018-11-16 2018-11-16 プレート式熱交換器、ヒートポンプ装置およびヒートポンプ式冷暖房給湯システム

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EP3882556A1 true EP3882556A1 (de) 2021-09-22
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Cited By (1)

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Publication number Priority date Publication date Assignee Title
EP4343252A1 (de) * 2022-09-20 2024-03-27 Alfa Laval Corporate AB Plattenwärmetauscher

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Publication number Priority date Publication date Assignee Title
JP7247717B2 (ja) * 2019-04-01 2023-03-29 株式会社デンソー 熱交換器
FR3122728B1 (fr) * 2021-05-06 2023-06-02 Commissariat A L’Energie Atomique Et Aux Energies Alternatives Module d’échangeur de chaleur à plaques à canaux intégrant au moins une zone d’alimentation et de distribution de fluide formée par des plots.
DE102022103720A1 (de) 2022-02-17 2023-08-17 Mahle International Gmbh Wärmeübertrager mit optimiertem Druckverlust
US20230400262A1 (en) * 2022-06-13 2023-12-14 Hamilton Sundstrand Corporation Supercooled thermal storage for high load short duration cooling
EP4343263A1 (de) * 2022-09-20 2024-03-27 Alfa Laval Vicarb Wärmetauschermodul

Family Cites Families (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE466027B (sv) * 1990-05-16 1991-12-02 Alfa Laval Thermal Ab Dubbelvaeggig plattvaermevaexlare med laeckagekanaler tvaers taetningspartierna
JPH04155191A (ja) * 1990-10-17 1992-05-28 Hitachi Ltd 積層形熱交換器
JPH07504966A (ja) * 1991-10-30 1995-06-01 レノックス　インダストリーズ　インコーポレイテッド 家庭用熱水を生産するための補助ヒートポンプ装置
CA2056678C (en) * 1991-11-29 1995-10-31 John G. Burgers Full fin evaporator core
JPH06123582A (ja) * 1992-10-09 1994-05-06 Mitsubishi Heavy Ind Ltd 積層型熱交換器
JP2605035Y2 (ja) * 1993-06-25 2000-06-19 昭和アルミニウム株式会社 積層型熱交換器
JPH1047879A (ja) * 1996-07-26 1998-02-20 Mitsubishi Materials Corp 熱交換器
JP2000310497A (ja) * 1999-04-27 2000-11-07 Toyo Radiator Co Ltd 高温ガス用カッププレート型熱交換器およびその製造方法
JP4605925B2 (ja) * 2001-03-08 2011-01-05 サンデン株式会社 積層型熱交換器
CA2383649C (en) * 2002-04-24 2009-08-18 Long Manufacturing Ltd. Inverted lid sealing plate for heat exchanger
US20140060789A1 (en) * 2008-10-03 2014-03-06 Modine Manufacturing Company Heat exchanger and method of operating the same
JP5414502B2 (ja) * 2009-12-17 2014-02-12 三菱電機株式会社 プレート式熱交換器及びヒートポンプ装置
SE536618C2 (sv) * 2010-10-22 2014-04-01 Alfa Laval Corp Ab Värmeväxlarplatta och plattvärmeväxlare
JP5298100B2 (ja) * 2010-11-15 2013-09-25 トヨタ自動車株式会社 車両用熱交換器
JP5747879B2 (ja) * 2012-08-01 2015-07-15 カルソニックカンセイ株式会社 熱交換器
CN104718423B (zh) * 2012-10-16 2017-03-01 三菱电机株式会社 板式热交换器以及具备该板式热交换器的冷冻循环装置
JP6126358B2 (ja) * 2012-11-08 2017-05-10 株式会社マーレ フィルターシステムズ 多板式オイルクーラ
JP6083222B2 (ja) * 2012-12-07 2017-02-22 ダイキン工業株式会社 コントローラ
JP6091601B2 (ja) * 2013-03-22 2017-03-08 三菱電機株式会社 プレート式熱交換器及びそれを備えた冷凍サイクル装置
JP5983565B2 (ja) * 2013-08-30 2016-08-31 株式会社デンソー 冷却器
WO2015129936A1 (ko) * 2014-02-26 2015-09-03 주식회사 포스비 반응기 및 열교환기용 체널형 스텍 및 그 제조 방법
JP2015203508A (ja) 2014-04-11 2015-11-16 パナソニックＩｐマネジメント株式会社 プレート式熱交換器
DE102015010310A1 (de) * 2015-08-08 2017-02-09 Modine Manufacturing Company Gelöteter Wärmetauscher und Herstellungsverfahren
JP6363555B2 (ja) * 2015-04-28 2018-07-25 株式会社デンソー アルミニウム製熱交換器
CN207703051U (zh) * 2017-12-27 2018-08-07 浙江银轮机械股份有限公司 一种u形通道的油冷器

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4343252A1 (de) * 2022-09-20 2024-03-27 Alfa Laval Corporate AB Plattenwärmetauscher
WO2024061817A1 (en) * 2022-09-20 2024-03-28 Alfa Laval Corporate Ab A plate heat exchanger

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JPWO2020100276A1 (ja) 2021-02-15
CN112997045A (zh) 2021-06-18
CN112997045B (zh) 2022-12-20
WO2020100276A1 (ja) 2020-05-22
US20210341186A1 (en) 2021-11-04
JP6529709B1 (ja) 2019-06-12
EP3882556B1 (de) 2023-10-11

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