EP3882556B1 - Plate-type heat exchanger, heat pump device, and heat-pump-type cooling/heating hot-water supply system - Google Patents
Plate-type heat exchanger, heat pump device, and heat-pump-type cooling/heating hot-water supply system Download PDFInfo
- Publication number
- EP3882556B1 EP3882556B1 EP18940018.7A EP18940018A EP3882556B1 EP 3882556 B1 EP3882556 B1 EP 3882556B1 EP 18940018 A EP18940018 A EP 18940018A EP 3882556 B1 EP3882556 B1 EP 3882556B1
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- EP
- European Patent Office
- Prior art keywords
- flow passage
- heat transfer
- plate
- projecting portion
- projecting
- Prior art date
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Images
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 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.
- 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 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 l2 (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 l2 of the inner fin 5, in this example, those heights may be equal to each other, or this relationship may be inverted.
- 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 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.
- 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.
- 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 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.
- Embodiment 3 differs from Embodiment 2, and omits to describe components of Embodiment 3 that are similar to those of Embodiment 2.
- 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 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).
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
- Details Of Fluid Heaters (AREA)
- Central Heating Systems (AREA)
Description
- 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.
- Hitherto, there has been known 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).
- In
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. Taking these circumstances into consideration, inPatent Literature 1, the wall surfaces in the gaps to inhibit the fluid from undesirably flowing into the gaps. DocumentUS 2003/201094 A1 discloses a plate-type heat exchanger according to the preamble ofclaim 1. - Patent Literature 1: Japanese Unexamined Patent Application Publication
JP 2015-203508 A - 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. - Incidentally, 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. However,
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 according to an embodiment of the present invention 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.
- According to an embodiment of the present invention, 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.
- Further, 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.
-
- 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. 5
- is a cross-sectional view taken along line A-A in
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 . - 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 . - 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 . - 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. 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 . - 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 . - 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 an area extending over a distance δ from a first line α.
- 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 δ from the first line α.
- 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 δ from the first line α. - 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.
- 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. - In the following, 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. - Moreover, the forms of components expressed in the entire text of the specification are merely examples, and are not limited to forms described herein. Further, a relationship in size between components in the following drawings may be different from an actual relationship in size between the components.
- Further, the terms showing directions (such as "upper", "lower", "right", "left", "front", and "back") used as appropriate for ease of understanding in the following description are intended for illustrative purposes, and are not intended to limit the present invention. Further, in
Embodiment 1, 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. Further, as for 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 toEmbodiment 1 of the present invention.FIG. 2 is a front view of a first heat transfer plate of the plate-type heat exchanger according toEmbodiment 1 of the present invention.FIG. 3 is a front view of a second heat transfer plate of the plate-type heat exchanger according toEmbodiment 1 of the present invention.FIG. 4 is a front perspective view of a heat transfer set of the plate-type heat exchanger according toEmbodiment 1 of the present invention. - Although
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-A inFIG. 4 .FIG. 6 is an end elevation view of a cross-section taken along line B-B inFIG. 4 .FIG. 7 is a cross-sectional view taken along line B-B inFIG. 4 .FIG. 8 is an end elevation view of a cross-section taken along line C-C inFIG. 4 . - As shown in
FIG. 1 , a plate-type heat exchanger 100 ofEmbodiment 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 afirst flow passage 6 through which a first fluid flows and asecond flow passage 7 through which a second fluid flows. - Moreover, an
inner fin 4 is disposed in theflow passage 6, and aninner fin 5 is disposed in thesecond flow passage 7. Thus, a heat transfer set 200 includes theinner fin 4, the firstheat transfer plate 1, theinner fin 5, and the secondheat transfer plate 2 being stacked starting from the front. The firstheat transfer plate 1, the secondheat transfer plate 2, theinner fin 4, and theinner 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 thefirst flow passage 6 and the second fluid flowing through thesecond 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 HFOmix or CO2. In
FIG. 1 , the first fluid is indicated by a solid arrow, and the second fluid is indicated by a dotted arrow. Further, although, inFIG. 1 , 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.
- Further, a 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. InFIG. 1 , the first reinforcingside plate 3 is a plate stacked on the foreground surface, and the second reinforcing side plate 8 is a plate stacked on the rearmost surface. - Further, as shown in
FIG. 1 , the first reinforcingside 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 reinforcingside 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. - In particular, a
first inflow pipe 9 through which the first fluid flows in is provided in the lower right corner of the first reinforcingside plate 3, and afirst outflow pipe 10 through which the first fluid flows out is provided in the lower left corner of the first reinforcingside plate 3. Further, asecond inflow pipe 11 through which the second fluid flows in is provided in the upper left corner of the first reinforcingside plate 3, and asecond outflow pipe 12 through which the second fluid flows out is provided in the upper right corner of the first reinforcingside plate 3. - Although
FIG. 1 shows a configuration in which the side plates are entirely uniform in wall thickness, the uniform configuration does not imply any limitation. For example, 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. - Further, although, in
FIG. 1 , the 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 secondheat transfer plate 2 have holes that face thefirst inflow pipe 9, thefirst outflow pipe 10, thesecond inflow pipe 11, and thesecond outflow pipe 12, respectively. Specifically, as shown inFIG. 2 , the firstheat transfer plate 1 is provided in the lower right corner thereof afirst inflow hole 13 through which the first fluid flows in, and is provided in the lower left corner thereof afirst outflow hole 14 through which the first fluid flows out. - The first
heat transfer plate 1 is provided in the upper left corner thereof asecond inflow hole 15 through which the second fluid flows in, and is provided in the upper right corner thereof asecond outflow hole 16 through which the second fluid flows out. Moreover, the firstheat transfer plate 1 has a cylindrically-shaped surrounding walls W provided around thesecond inflow hole 15 and thesecond outflow hole 16, and thesecond inflow hole 15 and thesecond outflow hole 16 are configured not to communicate with thefirst flow passage 6. This prevents the second fluid from flowing into thefirst flow passage 6 through thesecond inflow hole 15 and thesecond outflow hole 16. - Further, as shown in
FIG. 3 , the secondheat transfer plate 2 is provided in the lower right corner thereof afirst inflow hole 17 through which the first fluid flows in, and is provided in the lower left corner thereof afirst outflow hole 18 through which the first fluid flows out. The secondheat transfer plate 2 is provided with, in the upper left corner thereof, asecond inflow hole 19 through which the second fluid flows in, and is provided with, in the upper right corner thereof, asecond outflow hole 20 through which the second fluid flows out. - Moreover, the second
heat transfer plate 2 has cylindrically-shaped surrounding walls W provided around thefirst inflow hole 17 and thefirst outflow hole 18, and thefirst inflow hole 17 and thefirst outflow hole 18 are configured not to communicate with thesecond flow passage 7. This prevents the first fluid from flowing into thesecond flow passage 7 through thefirst inflow hole 17 and thefirst outflow hole 18. - The first
heat transfer plate 1 and the secondheat transfer plate 2 are hereinafter referred to collectively as "heat transfer plates" when it is not necessary to distinguish between them. Further, the first reinforcingside 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. Further, thefirst flow passage 6 and thesecond flow passage 7 are hereinafter referred to collectively as "flow passages" when it is not necessary to distinguish between them. - Further, the term "first direction" refers to a direction of flow of a fluid, that is, a horizontal direction of
FIG. 1 , and the term "second direction" refers to a direction orthogonal to the first direction, that is, a vertical direction ofFIG. 1 . - As shown in
FIG. 5 , each of the heat transfer plates has aflat portion 30 andouter wall portions 31 extending outward from both ends of theflat portion 30 in the second direction, and theouter 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 eachflat portion 30 and an adjacentflat portion 30, and this space serves as thefirst flow passage 6 or thesecond flow passage 7. InFIG. 5 , thefirst flow passage 6 is located above the firstheat transfer plate 1, and thesecond flow passage 7 is located between the firstheat transfer plate 1 and the secondheat transfer plate 2. Further, as shown inFIGS. 2 and 3 , each of the heat transfer plates hasheader portions 24 provided at both ends thereof in the first direction. - While 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 (seeFIG. 5 ) that is equal to a flow passage height of thefirst flow passage 6, and is in contact with theflat portion 30 of the firstheat transfer plate 1 and theflat portion 30 of the secondheat transfer plate 2. The points of contact may be joined, for example, by brazing or may not be joined. Further, theinner fin 5 has a height l2 (seeFIG. 5 ) that is equal to a flow passage height of thesecond flow passage 7, and is in contact with theflat portion 30 of the firstheat transfer plate 1 and theflat portion 30 of the secondheat transfer plate 2. Although the height l1 of theinner fin 4 is greater than the height l2 of theinner 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 andhorizontal 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. - For convenience in manufacturing of the plate-type heat exchanger by automatic assembling,
gaps 21 are formed between both ends of theinner fin 4 in the second direction and both ends of the firstheat transfer plate 1 in the second direction or, specifically, theouter wall portions 31. The first fluid having flowed into thefirst flow passage 6 through thefirst inflow hole 13 of the firstheat transfer plate 1 easily flows into thegaps 21, as the first fluid is subjected to a weaker resistance than in a case where it flows into theinner fin 4. For this reason, the first fluid preferentially flows into thegaps 21 without uniformly flowing through thefirst flow passage 6. This deteriorates heat exchange performance. - In order to solve this problem, the first
heat transfer plate 1 has first projectingportions 22 provided upstream of thegaps 21. Specifically, the first projectingportions 22 are provided upstream of an edge of theinner fin 4 through which the fluid flows in and at both ends of the firstheat transfer plate 1 in the second direction. The first projectingportions 22 are formed by projecting portions projecting from theflat portion 30 of the firstheat transfer plate 1 toward thefirst flow passage 6, and are formed by press working. The first projectingportions 22 prevent the first fluid from flowing into thegaps 21. - Further, the first
heat transfer plate 1 has a second projectingportion 23 provided downstream of an edge of theinner fin 4 through which the fluid flows out. In other words, the second projectingportion 23 is provided in a location at a length of the firstheat transfer plate 1 in the first direction from the first projectingportions 22. The second projectingportion 23 includes a projecting portion projecting from theflat portion 30 of the firstheat transfer plate 1 toward thefirst flow passage 6, and is formed by press working. The second projectingportion 23 may be located off the central part of the firstheat transfer plate 1 in the second direction as shown inFIG. 2 or may be located in the central part, and is not limited to any particular location in the second direction. - By thus providing the first
heat transfer plate 1 with the second projectingportion 23 in addition to the first projectingportions 22, the locations of both ends of theinner fin 4 in the first direction are determined, so that theinner fin 4 can be positioned in the first direction in being placed onto the firstheat transfer plate 1. In this example, the first projectingportions 22 and the second projectingportion 23 are each formed in a circular shape. However, the first projectingportions 22 and the second projectingportion 23 are limited to a circular shape. The first projectingportions 22 and the second projectingportion 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. - Further, along with the automatic assembling of the plate-type heat exchanger, gaps 25 (see
FIG. 5 ) are similarly formed between both ends of theinner fin 5 in the second direction and both ends of the secondheat transfer plate 2 in the second direction or, specifically, theouter wall portions 31. The second fluid having flowed into thesecond flow passage 7 through thesecond inflow hole 19 of the secondheat transfer plate 2 easily flows into thegaps 25, as the second fluid is subjected to a weaker resistance than in a case where it flows into theinner fin 5. For this reason, the second fluid preferentially flows into thegaps 25 without uniformly flowing through thesecond flow passage 7. This causes a decrease in heat exchange performance. - To address this problem, the second
heat transfer plate 2 has first projectingportions 26 provided upstream of thegaps 25. Specifically, the first projectingportions 26 are provided upstream of an edge of theinner fin 5 through which the fluid flows in and at both ends of the secondheat transfer plate 2 in the second direction. The second projectingportions 26 include projecting portions projecting from theflat portion 30 of the secondheat transfer plate 2 toward thesecond flow passage 7, and are formed by press working. The first projectingportions 26 prevent the second fluid from flowing into thegaps 25. - Further, the second
heat transfer plate 2 has a second projectingportion 27 provided downstream of an edge of theinner fin 5 through which the fluid flows out. In other words, the second projectingportion 27 is provided in a location at a length of the secondheat transfer plate 2 in the first direction from the first projectingportions 26. The second projectingportion 27 is formed by a projecting portion projecting from theflat portion 30 of the secondheat transfer plate 2 toward thesecond flow passage 7, and is formed by press working. The second projectingportion 27 may be located off the central part of the secondheat transfer plate 2 in the second direction as shown inFIG. 3 or may be located in the central part, and is not limited to any particular location in the second direction. - By thus providing the second
heat transfer plate 2 with the second projectingportion 27 in addition to the first projectingportions 22, the locations of both ends of theinner fin 5 in the first direction are determined, so that theinner fin 5 can be positioned in the first direction in being placed onto the secondheat transfer plate 2. In this example, the first projectingportions 26 and the second projectingportion 27 are each formed in a circular shape. However, the first projectingportions 26 and the second projectingportion 27 are not limited to being circular in shape. The first projectingportions 26 and the second projectingportion 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. - Note here that as shown in
FIG. 5 , theinner fin 4 has a shape of asperities in fine cycles. Spacings between twovertical walls 32 of theinner 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 theinner fin 4 can be performed with an end of theinner fin 4 in the first direction surely in contact with the first projectingportions 22, it is desirable that as shown inFIG. 7 , the width ψ of each of the first projectingportions 22 be twice or more as great as the distance χ between two adjacentvertical walls 32 of theinner fin 4. Making the width ψ of each of the first projectingportions 22 twice or more as great as the distance χ between the twovertical walls 32 means that the width ψ of each of the first projectingportions 22 is greater than or equal to one cycle of asperities of theinner fin 4. - The
inner fin 4 is designed to get the most out of the width of theflat portion 30 of the heat transfer plate in the second direction. Therefore, the difference between the width of theinner fin 4 in the second direction and the width of theflat portion 30 in the second direction is shorter than one cycle of asperities of theinner fin 4. Therefore, by making the width ψ of each of the first projectingportions 22 twice or more as great as the distance χ between the twovertical walls 32, positioning of theinner fin 4 can be performed with the end of theinner fin 4 in the first direction surely in contact with the first projectingportions 22. - Note here that an increase in the width ψ of each of the first projecting
portions 22 leads to an increase in ease of positioning of theinner fin 4 but results in the formation of a portion in theinner fin 4 into which the fluid hardly flows. For example, using as the inner fin 4 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. Such a problem can be prevented by using a fin, such as an offset fin, configured such that a fluid both flows in a mainstream direction (indicated by an arrow inFIG. 2 ) and moderately flows in a direction of flow that intersects the mainstream direction. - Further, even in a case where an offset fin is used as the
inner fin 4, too large a width ψ of each of the first projectingportions 22 may lead to an increase in area of insufficient inflow of the first fluid into theinner fin 4. Accordingly, it is desirable that the width ψ of each of the first projectingportions 22 be five times or less as great as the distance χ between two adjacentvertical walls 32 of theinner fin 4. - This makes it possible to reduce the area of insufficient inflow of the first fluid into the
inner fin 4. Note here that it is for the following reason that the width ψ of each of the first projectingportions 22 is made five times or less as great as the distance χ between two adjacentvertical walls 32 of theinner fin 4. The width ψ of each of the first projectingportions 22 is made five times or less as great as the distance χ, as flow through a fin portion is affected when the width ψ is more than five times as great as the distance χ. - Although the foregoing has described the first projecting
portions 22, the same applies to the first projectingportions 26 formed on the secondheat transfer plate 2. That is, the width ψ of each of the first projectingportions 26 is twice or more and five times or less as great as the distance χ between two adjacentvertical walls 32 of theinner fin 5. Further, although the foregoing has described the first projectingportions 22 and the first projectingportions 26, the same applies to the second projectingportion 23 and the second projectingportion 27. That is, it is preferable that the width ψ of each of the second projectingportions vertical walls 32 of the inner fin. - Further, although, in
FIG. 7 , the height h of each of the first projectingportions 22 is smaller than the height l of the inner fin 4 (h < 11), the height h of each of the first projectingportions 22 may be at most equal to the height l of the inner fin 4 (h = 11). In a case where the height h of each of the first projectingportions 22 is equal to theheight 11 of theinner fin 4, the flow of the first fluid in thegaps 21 can be further inhibited than in a case where the height h is smaller than theheight 11. In a case where the height h of each of the first projectingportions 22 is smaller than theheight 11 of the inner fin 4 (h < 11), the first projectingportions 22 do not make contact with the secondheat transfer plate 2, but in a case where the height h of each of the first projectingportions 22 is equal to the height of the inner fin 4 (h = 11), the first projectingportions 22 make contact with the secondheat transfer plate 2. These points of contact may be joined, for example, by brazing or may not be joined. - It is desirable to bring about improvement in structural strength of the
second flow passage 7, as the high-pressure second fluid passes through thesecond flow passage 7. For this reason, it is desirable to set up a configuration in which the height of each of the first projectingportions 26 be equal to the height l2 of theinner fin 5 and points of contact between end faces of the first projectingportions 26 and the firstheat transfer plate 1 are joined, for example, by brazing. - While the forgoing has assumed that the first projecting
portions 22 are located upstream of the edge of theinner fin 4 through which the fluid flows in and at both ends of the firstheat transfer plate 1 in the second direction, the following more specifically describes the locations of the first projectingportions 22. A specific scope of "both ends of the firstheat transfer plate 1 in the second direction" is described with reference toFIG. 4 . Each first projectingportion 22 is provided within an area surrounded by a first line α representing an inflow edge of both edges of theinner fin 4 in the first direction, two second lines β representing both edges of theflat portion 30 in the second direction, and twocircular arcs 28 indicated by dotted lines inFIG. 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 α and a corresponding one of the second lines β, and the radius R is three times as great as the flow passage height l1 of thefirst flow passage 6. The placement of the first projectingportions 22 in the aforementioned locations makes it possible to enhance the effect of inhibiting the first fluid from flowing into thegaps 21. - Note that the
gaps 21 between theinner fin 4 and theouter wall portions 31 each measure approximately 1 mm. The height l1 of theinner fin 4 is approximately 0.5 mm to 2.5 mm. A "triple" of the height l1 of theinner fin 4 ranges from 1.5 mm to 7.5 mm. The distance between two adjacentvertical walls 32 of theinner fin 4 is approximately 0.5 mm to 1.5 mm. - The width ψ of each of the first projecting
portions 22 is approximately 1.0 mm to 7.5 mm, as it is desirable that the width ψ of each of the first projectingportions 22 be twice or more and five times or less as great as the distance between two adjacentvertical walls 32 of theinner fin 4. Therefore, for minimization of thegaps 21 between theinner fin 4 and theouter wall portions 31 and enhancement of the effect of inhibiting the flow rate of the first fluid that flows into thegaps 21, the radius R is made three times as great as theflow passage height 11 of thefirst flow passage 6. - Although the foregoing has described the specific scope of "both ends of the first
heat transfer plate 1 in the second direction" in relation to the locations of the first projectingportions 22, the same applies to the locations of the first projectingportions 26 of the secondheat transfer plate 2. That is, each first projectingportion 26 is provided within an area surrounded by a first line representing an inflow edge of both edges of theinner fin 5 in the first direction, two second lines representing both edges of theflat 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 l2 of thesecond flow passage 7. - The following describes the flow of the fluids through the plate-
type heat exchanger 100 thus configured and the action of the first projectingportions 22 and the first projectingportions 26. - The first fluid having flowed into the
first inflow pipe 9 from outside flows into thefirst flow passage 6 via thefirst inflow hole 13 of the firstheat transfer plate 1. The first fluid having flowed into thefirst flow passage 6 flows through theinner fin 4 in a direction from right to left as indicated by a solid arrow inFIG. 2 while gradually spreading toward theouter wall portions 31 of the firstheat transfer plate 1 and flows out from thefirst outflow pipe 10 via thefirst outflow hole 14 of the firstheat transfer plate 1. - The second fluid having flowed into the
second inflow pipe 11 from outside flows into thesecond flow passage 7 via thesecond inflow hole 19 of the secondheat transfer plate 2. The second fluid having flowed into thesecond flow passage 7 flows through theinner fin 5 in a direction from left to right as indicated by a dotted arrow inFIG. 3 while spreading toward theouter wall portions 31 of the secondheat transfer plate 2 and flows out from thesecond outflow pipe 12 via thesecond outflow hole 20 of the secondheat transfer plate 2. - Thus, the flow of the first fluid through the
first flow passage 6 and the flow of the second fluid through thesecond flow passage 7 allow the first fluid and the second fluid to exchange heat with each other via the firstheat transfer plate 1 and the secondheat transfer plate 2. - Note that the provision of the first projecting
portions 22 in thefirst flow passage 6 prevents the first fluid of thefirst flow passage 6 from flowing into thegaps 21. This makes it possible to rectify an imbalance of the first fluid in thefirst flow passage 6 and bring about improvement in distributive performance to both the upper and lower sides ofFIG. 2 . - Further, the same applies to the
second flow passage 7. That is, the provision of the first projectingportions 26 in thesecond flow passage 7 prevents the second fluid flowing through thesecond flow passage 7 from flowing into thegaps 25. This makes it possible to rectify an imbalance of the second fluid in thesecond flow passage 7 and bring about improvement in distributive performance to both the upper and lower sides ofFIG. 3 . - By thus providing the first projecting
portions 22 and the first projectingportions 26 in thefirst flow passage 6 and thesecond flow passage 7, respectively, 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. - As described above, according to
Embodiment 1, the first projectingportions 22 are provided on an inflow side of the firstheat transfer plate 1. This makes it possible to inhibit the first fluid from preferentially flowing into thegaps 21 and improve the in-plane distributive performance of the first fluid in thefirst flow passage 6. Further, the second projectingportion 23, which performs positioning in placing theinner fin 4 into thefirst flow passage 6, is provided on an outflow side of the firstheat transfer plate 1. - This makes it possible to determine the location of the
inner fin 4 with the first projectingportions 22 and the second projectingportion 23. Since the first projectingportions 22 and the second projectingportion 23 are formed by press working, these effects can be achieved without addition of attachments. This makes it possible to achieve an increase in performance and a reduction in cost of the plate-type heat exchanger. - Further, the same applies to the second
heat transfer plate 2. That is, the provision of the first projectingportions 26 and the second projectingportion 27 makes it possible to determine the location of theinner fin 5 while improving the in-plane distributive performance of the second fluid without addition of attachments. - Further, the joining of a portion of the second projecting
portion 27 that is in contact with the firstheat transfer plate 1 and the secondheat transfer plate 2 makes it possible to bring about improvement in strength. - Thus, in the
first flow passage 6 or thesecond flow passage 7, the positioning of theinner fin 4 or theinner 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 andhorizontal 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 adjacentvertical walls 32 of the inner fin. - This makes it possible to position the inner fin with an end of the inner fin in the first direction surely in contact with the first projecting portions. Further, 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. - Further, 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.
- Since the first projecting portions, which are provided on the inflow sides of the heat transfer plates, and the second projecting portions, which are provided on the outflow sides of the heat transfer plates, are provided in both the first flow passage and the second flow passage, improvement in in-plane distributive performance can be brought about in both the first flow passage and the second flow passage.
- The first projecting
portions 22 of thefirst flow passage 6 and the second projectingportion 27 of thesecond 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 projectingportion 23 of thefirst flow passage 6 and the first projectingportions 26 of thesecond 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.
- In
Embodiment 1, the second projectingportion 23 and the second projectingportion 27 are each formed in one place. InEmbodiment 2, second projectingportions 23 are formed in two places, and second projectingportions 27 are formed in two places. The following mainly describes points in whichEmbodiment 2 differs fromEmbodiment 1, and omits to describe constituent elements ofEmbodiment 2 that are similar to those ofEmbodiment 1. -
FIG. 9 is a front perspective view of a heat transfer set of a plate-type heat exchanger according toEmbodiment 2 of the present invention.FIG. 10 is an end elevation view of a cross-section taken along line B-B inFIG. 9 .FIG. 11 is an end elevation view of a cross-section taken along line C-C inFIG. 9 . -
Embodiment 2 is identical toEmbodiment 1 except for the numbers and locations of second projectingportions 23 and second projectingportions 27. - As shown in
FIGS. 9 and11 , the firstheat transfer plate 1 of the heat transfer set 200 ofEmbodiment 2 has second projectingportions 23 provided in locations at a length of theinner fin 4 in the first direction from the first projectingportions 22 and at both ends of the firstheat transfer plate 1 in the second direction. Further, the secondheat transfer plate 2 has second projectingportions 27 provided in locations at a length of theinner fin 4 in the first direction from the first projectingportions 26 and, as shown inFIG. 10 , at both ends of the secondheat transfer plate 2 in the second direction. -
Embodiment 2 brings about the same effects asEmbodiment 1 and, in addition, brings about the following effects. That is, whileEmbodiment 1 has one second projectingportion 23 and one second projectingportion 27,Embodiment 2 has two second projectingportions 23 provided at both ends of a heat transfer plate in the second direction and two second projectingportions 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 thefirst flow passage 6, and the second projectingportions 27 are located on an outflow side of thesecond flow passage 7. Therefore, in thefirst flow passage 6, outflow sides of thegaps 21, which extend in a horizontal direction, are closed by the second projectingportions 23, and in thesecond flow passage 7, outflow sides of thegaps 25, which extend in a horizontal direction inFIG. 9 , are closed by the second projectingportions 27. - This configuration makes it possible to prevent more effectively the first fluid from flowing into the
gaps 21 and the second fluid from flowing into thegaps 25 than the configuration ofEmbodiment 1 in which only inflow sides of thegaps 21 and thegaps 25 are closed. As a result,Embodiment 2 can bring about further improvement in in-plane distributive performance thanEmbodiment 1. This makes it possible to achieve an increase in performance of the plate-type heat exchanger 100. - Although the foregoing description has been made presuming that the second projecting
portions 23 are located at "both ends of the firstheat transfer plate 1 in the second direction" and that the second projectingportions 27 are located at "both ends of the secondheat transfer plate 2 in the second direction", a specific scope of these locations are basically the same as the scope of the first projectingportions 22 and the first projectingportions 26 described inEmbodiment 1. - That is, each second projecting
portion 23 is provided within an area surrounded by a third line γ representing an outflow edge of both edges of theinner fin 4 in the first direction, two second lines β, and twocircular arcs 28. Each of thecircular arcs 28 is a circular arc with a radius R centered at a point of intersection O of the third line γ and a corresponding one of the second lines β, and the radius R is three times as large as theflow passage height 11 of thefirst flow passage 6. - Further, each second projecting
portion 27 is provided within an area surrounded by a third line representing an outflow edge of both edges of theinner fin 5 in the first direction, two second lines β, 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 β, and the radius R is three times as large as the flow passage height l2 of thesecond 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 ofFIG. 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 ofFIG. 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 ofFIG. 9 . - The first
heat transfer plate 1 and the secondheat transfer plate 2 of the modification shown inFIGS. 12 and13 each include two plates partially joined to each other. Specifically, the firstheat transfer plate 1 includesplates 1a and 1b partially joined to each other. The secondheat transfer plate 2 includesplates FIGS. 12 to 14 ,black portions 29 between plates indicate junctions. - By 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 toEmbodiment 2 but also toEmbodiment 1 andEmbodiment 3, which is described below. - The following mainly describes points in which
Embodiment 3 differs fromEmbodiment 2, and omits to describe components ofEmbodiment 3 that are similar to those ofEmbodiment 2. -
FIG. 15 is a front perspective view of a heat transfer set of a plate-type heat exchanger according toEmbodiment 3 of the present invention. AlthoughFIG. 15 is a perspective view,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 ofFIG. 15 .FIG. 17 is a cross-sectional view taken along line A-A inFIG. 15 .FIG. 18 is an end elevation view of a cross-section taken along line B-B inFIG. 15 .FIG. 19 is an end elevation view of a cross-section taken along line C-C inFIG. 15 . It should be noted that the opposite ofEmbodiment 2 is true inFIG. 15 ; that is, the secondheat transfer plate 2 is situated at the front, and the firstheat transfer plate 1 is situated at the back. - As in the case of
Embodiment 2, the secondheat transfer plate 2 has circular first projectingportions 26 provided on an inflow side thereof and circular second projectingportions 27 provided on an outflow side thereof. The first projectingportions 26 and the second projectingportions 27 are in contact with the firstheat transfer plate 1, and these points of contact are joined, for example, by brazing. - The first projecting
portions 26 and the second projectingportions 27 are equal in height to theinner fin 5. Moreover, the secondheat transfer plate 2 ofEmbodiment 3 further has circular arc first depressedportions 40 formed to surround inflow sides of the first projectingportions 26. Further, the secondheat transfer plate 2 ofEmbodiment 3 further has circular arc seconddepressed portions 41 formed to surround outflow sides of the second projectingportions 27. - As shown in
FIGS. 18 and 19 , the firstdepressed portions 40 and the seconddepressed portions 41 include depressed portions depressed from the secondheat transfer plate 2 toward thefirst flow passage 6. The firstdepressed portions 40 and the seconddepressed portions 41 are half as high as theinner fin 4. - The first
heat transfer plate 1 has circular arc first projectingportions 22a and circular arc second projectingportions 23a formed instead of the circular first projectingportions 22 and the circular second projectingportions 23 ofEmbodiment 2. As shown inFIGS. 18 and 19 , the first projectingportions 22a and the second projectingportions 23a include projecting portions projecting from the firstheat transfer plate 1 toward thefirst flow passage 6. The projectingportions 22a and the second projectingportions 23a are half as high as theinner fin 4. The first projectingportions 22a and the second projectingportions 23a are in contact with the seconddepressed portions 41 and the firstdepressed portions 40, respectively, of the secondheat transfer plate 2, and these points of contact are joined, for example, by brazing. - Thus, in the plate-
type heat exchanger 100 according toEmbodiment 3, the circular arc projecting portions formed on the firstheat transfer plate 1 and the circular projecting portions formed on the secondheat transfer plate 2 are different in shape from each other. - Such a configuration of the first
heat transfer plate 1 and the secondheat transfer plate 2 causes circular arc flow passage blocking portions to be formed by contact between the seconddepressed portions 41 and the first projectingportions 22a upstream of thegaps 21 in thefirst flow passage 6, so that the inflow of the first fluid into thegaps 21 can be inhibited. Similarly, circular arc flow passage blocking portions are formed by contact between the firstdepressed portions 40 and the second projectingportions 23a downstream of thegaps 21. That is, the flow passage blocking portions are formed both upstream and downstream of thegaps 21. This configuration makes it possible to better prevent the first fluid from flowing into thegaps 21 than a configuration in which flow passage blocking portions are provided only upstream of thegaps 21. - Further, as in the case of
Embodiment 2, the first projectingportions 26 and the second projectingportions 27 are provided upstream and downstream, respectively, of thegaps 25 in thesecond flow passage 7. This makes it possible to inhibit the second fluid from flowing into thegaps 25. - Although
Embodiment 3 has illustrated a configuration in which the circular arc first projectingportions 22a and the circular arc second projectingportions 23a are formed on the firstheat transfer plate 1 and the circular projectingportions 26, the circular second depressed portions, the circular arc first depressedportions 40, and the circular arc seconddepressed portions 41 are formed on the secondheat transfer plate 2, the opposite may be true. - That is, there may be a configuration in which the circular projecting
portions 26, the circular seconddepressed portions 27, the circular arc first depressedportions 40, and the circular arc seconddepressed portions 41 are formed on the firstheat transfer plate 1 and the circular arc first projectingportions 22a and the circular arc second projectingportions 23a are formed on the secondheat transfer plate 2. - Further, according to
Embodiment 3, in the firstheat transfer plate 1, improvement in in-plane distributive performance in thefirst flow passage 6 and positioning of theinner fin 4 are simultaneously achieved by the first projectingportions 22a and the second projectingportions 23a. Further, in the secondheat transfer plate 2, improvement in in-plane distributive performance and positioning of theinner fin 5 are simultaneously achieved by the first projectingportions 26 and the second projectingportions 27. - The first projecting
portions 22a and the second projectingportion 23a are not limited to being circular arc in shape. The first projectingportions 22a and the second projectingportion 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. - As described above,
Embodiment 3 brings about the same effects asEmbodiment 2 and brings about the following effects. That is, the structure in which the firstheat transfer plate 1 and the secondheat transfer plate 2 are joined at theflat portions 30 by a combination of projecting portions and depressed portions brings about improvement in strength. Further, since the first projectingportion 22a and the second projectingportions 23a of thefirst flow passage 6 are half as high as thefirst 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. - That is, because of the percentages of elongation of the heat transfer plates, the
first flow passage 6 composed of projecting portions ofEmbodiment 3 can be made twice as high as thefirst flow passage 6 composed of projecting portions ofEmbodiment 1. This makes it possible to easily achieve optimization of the height of thefirst flow passage 6 composed of projecting portions ofEmbodiment 3. Alternatively, this makes it possible to more easily achieve optimization of the size of the first projectingportions 22a and the second projectingportions 23a and the height of thefirst 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 firstheat transfer plate 1 and the second projectingportions 27 of the secondheat 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. - Further, the second projecting
portions 23a of the firstheat transfer plate 1 and the first projectingportions 26 of the secondheat 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. Thus, 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 theheader portions 24 with projecting and depressed structures. The following mainly describes points in whichEmbodiment 4 differs fromEmbodiment 1, and omits to describe components ofEmbodiment 4 that are similar to those ofEmbodiment 1. -
FIG. 20 is a partial front perspective view of a heat transfer set of a plate-type heat exchanger according toEmbodiment 4 of the present invention.FIG. 21 is a cross-sectional view taken along line D-D inFIG. 20 . - The
header portions 24 provided on the inflow and outflow sides, respectively, of the firstheat transfer plate 1 are provided with a plurality ofdepressed portions 50 dispersed. Further, theheader portions 24 provided on the inflow and outflow sides, respectively, of the secondheat transfer plate 2 are provided with a plurality ofdepressed portions 51 facing thedepressed portions 50. - Top faces of the projecting
portions 51 are in contact with bottom faces of thedepressed portions 50, and these points of contact are joined. By thus providing theheader portions 24 with projecting anddepressed structures 52, improvement in strength of theheader portions 24 is brought about. Thedepressed portions 50 and the projectingportions 51 are formed in circular shapes and configured to be equal in diameter and height to each other. - For the prevention of blockage of the flow of the first fluid flowing out from the
inner fin 4, thedepressed portions 50 are not provided in an area in the outflow-side header portion 24 extending over a distance δ from the third line γ of theinner fin 4. Similarly, thedepressed portions 50 are not provided in an area in the inflow-side header portion 24 extending over the distance δ from the first line α of theinner fin 4. - Similarly, for the prevention of blockage of the flow of the second fluid flowing out from the
inner fin 5, the projectingportions 51 are not provided in an area in the outflow-side header portion 24 extending over the distance δ from the third line γ of theinner fin 5, although not illustrated. Similarly, thedepressed portions 50 are not provided in an area in the inflow-side header portion 24 extending over the distance δ from the first line α of theinner fin 5. - Note here that it is desirable that the distance δ 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 projectingportion 51 along a surface perpendicular to the first direction through the center of the junction:depressed portion 50 and the projectingportion 51 and l is the height of the junction between thedepressed portion 50 and the projectingportion 51. - The configuration in which no projecting and
depressed structure 52 is provided in the area extending over the distance δ from the first line α makes it possible to better uniform a velocity distribution of the fluid into the inner fin than a configuration in which a projecting anddepressed structure 52 is provided in the area extending over the distance δ from the first line α. This point was demonstrated by a test whose results are shown below. The following shows results of a test conducted on thesecond flow passage 7. -
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 δ from the first line α.FIG. 22 is equivalent to a velocity distribution in a cross-sectional taken along line F-F inFIG. 23 below. InFIG. 22 , the horizontal axis represents the second direction of the inner fin, and 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 δ from the first line α. - In
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 toEmbodiment 4 of the present invention in a case where no projecting and depressed structure is provided in the area extending over the distance δ from the first line α. In each ofFIGS. 23 and24 , the horizontal axis X represents the second direction of the inner fin, the vertical axis Y represents the first direction of the inner fin, and the arrows indicate the magnitude of the flow velocity. - As is clear from a comparison between
FIGS. 22 and 23 of the comparative example andFIG. 24 ofEmbodiment 4,Embodiment 4, which is configured such that no projecting anddepressed structure 52 is provided in the area extending over the distance δ from the first line α, ensures uniformity of flow velocity across theinner fin 5 in the second direction. -
FIGS. 22 to 24 are diagrams for making a comparison between a case where a projecting anddepressed structure 52 is provided in the area extending over the distance δ from the first line α and a case where no projecting anddepressed structure 52 is provided in the area extending over the distance δ from the first line α, and the first projectingportions 26, which serve to inhibit the inflow of the second fluid into thegaps 25 at both ends of thesecond flow passage 7, are not provided. For this reason, the flow velocity is high at both ends of theinner fin 5 in the second direction. Next,FIG. 25 shows a flow velocity distribution in a case where the first projectingportions 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. InFIG. 25 , the horizontal axis X represents the second direction of the inner fin, the vertical axis Y represents the first direction of the inner fin, and 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 anddepressed structure 52 is provided in the area extending over the distance δ from the first line α. - As shown in
FIG. 25 , the provision of the first projectingportions 26 makes the flow velocity in the gaps at both ends of thesecond flow passage 7 lower than it is inFIG. 24 . - Although the foregoing has described a flow velocity distribution of the fluid in the
second flow passage 7, the same tendency is seen in thefirst flow passage 6. - As described above,
Embodiment 4 brings about the same effects asEmbodiment 1 by providing the first projecting portions and can bring about improvement in strength of theheader portions 24 by providing theheader portions 24 with the projecting anddepressed structures 52. - Providing the
header portions 24 with the projecting anddepressed structures 52 in proximity to the inner fin causes non-uniformity of flow velocity of the fluid flowing into the inner fin. However,Embodiment 4 is configured such that the projecting anddepressed structures 52 are not provided at least in the areas extending over the distance δ from the first line α and the third line γ, respectively. This makes it possible to rectify a problem of a decrease in in-plane distributive performance caused by providing theheader portions 24 with the projecting anddepressed structures 52 and ensure uniformity of flow velocity of the fluid across the inner fin in the second direction. - Although the foregoing has described
Embodiments 1 to 4 as separate embodiments, features of the embodiments may be combined as appropriate to constitute a plate-type heat exchanger 100. For example,Embodiment 1 andEmbodiment 3 may be combined such that the width of each of the first and second projectingportions 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. - Further,
Embodiment 3 andEmbodiment 4 may be combined to be configured such that theheader portions 24 of the heat transfer set 200 ofEmbodiment 3 shown inFIG. 15 are provided with the projecting anddepressed structures 52 ofEmbodiment 4. A modification that is applied to the same constituent element of each ofEmbodiments 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 inEmbodiments 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 toEmbodiment 5 of the present invention. - A heat-pump-type cooling and heating hot-
water supply system 300 includes aheat pump device 65 and aheat medium circuit 70, and theheat pump device 65 includes arefrigerant circuit 60. Therefrigerant circuit 60 includes acompressor 61, aheat exchanger 62, adecompression device 63, and a heat exchanger being connected in sequence by pipes, and thedecompression device 63 is formed of, for example, by an expansion valve or a capillary tube. Theheat medium circuit 70 includes theheat exchanger 62, a cooling and heating hot-water supply device 71, and apump 72 being connected in sequence by pipes, and thepump 72 circulates a heat medium. Thecompressor 61, theheat exchanger 62, thedecompression device 63, and theheat exchanger 64 are housed in a housing of theheat pump device 65. - Note here that the
heat exchanger 62 is the plate-type heat exchanger 100 described above inEmbodiments 1 to 4, and carries out a heat exchange between refrigerant flowing through therefrigerant circuit 60 and the heat medium flowing through theheat medium circuit 70. The heat medium that is used in theheat 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 therefrigerant circuit 60. - Further, 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 HFOmix may be used as the refrigerant. - The plate-
type heat exchanger 100, which includes theheat exchanger 62, is incorporated into the heat-pump-type cooling and heating hot-water supply system 300 so that the refrigerant flows through thesecond flow passage 7, which is higher in heat-transfer performance than thefirst flow passage 6, and the heat medium flows through thefirst flow passage 6. Since theinner fin 4 and theinner fin 5 are equal in heat-transfer area to each other and theinner fin 5 is smaller in hydraulic diameter than theinner fin 4, thesecond flow passage 7 is higher in heat-transfer performance than thefirst 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. In a case where the cooling and heating hot-water supply device 71 is a hot water storage tank, the heat medium is water. The water is heated by theheat exchanger 62 exchanging heat with the refrigerant of therefrigerant circuit 60. The water thus heated is stored in the hot water storage tank (not illustrated). - Alternatively, in a case where the 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 theheat 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 theheat medium circuit 70. - In a case where heating and hot-water supply is performed, the
heat exchanger 62 is used as a condenser, and in the case of cooling, theheat exchanger 62 is used as an evaporator. Arrows shown inFIG. 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). - In a case where the
heat exchanger 62 is used as an evaporator, the refrigerant flows into thesecond flow passage 7 of theheat 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 projectingportions 22 from flowing into thegaps 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 ofEmbodiments 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 CO2. -
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. However, 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. - As an example of utilization of the present invention, 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. -
- 1
- heat transfer plate 1a plate
- 1b
- plate
- 2
- second heat transfer plate
- 2a
- plate
- 2b
- plate
- 3
- first reinforcing side plate
- 4
- inner fin
- 5
- inner fin
- 6
- first flow passage
- 7
- second flow passage
- 8
- second reinforcing side plate
- 9
- first inflow pipe
- 10
- first outflow pipe
- 11
- second inflow pipe
- 12
- second outflow pipe
- 13
- first inflow hole
- 14
- first outflow hole
- 15
- second inflow hole
- 16
- second outflow hole
- 17
- first inflow hole
- 18
- first outflow hole
- 19
- second inflow hole
- 20
- second outflow hole
- 21
- gap
- 22
- first projecting portion
- 22a
- first projecting portion
- 23
- second projecting portion
- 23a
- second projecting portion
- 24
- header portion
- 25
- gap
- 26
- first projecting portion
- 27
- second projecting portion
- 28
- circular arc
- 29
- black portion
- 30
- flat portion
- 31
- outer wall portion
- 40
- first depressed portion
- 41
- second depressed portion
- 50
- depressed portion
- 51
- projecting portion
- 52
- projecting and depressed structure
- 60
- refrigerant circuit
- 61
- compressor
- 62
- heat exchanger
- 63
- decompression device
- 64
- heat exchanger
- 65
- heat pump device
- 70
- heat medium circuit
- 71
- cooling and heating hot-water supply device
- 72
- pump
- 100
- plate-type heat exchanger
- 200
- heat transfer set
- 300
- heat-pump-type cooling and heating hot-water supply system
Claims (18)
- A plate-type heat exchanger (100) comprising:- 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; and- an inner fin (4, 5) disposed in the flow passage;characterised in that the plate-type heat exchanger (100) further comprises:- a first projecting portion (22) provided on an inflow side of each of the heat transfer plates and configured to prevent the fluid from flowing into gaps (25) between both ends of the inner fin (4, 5) in a second direction and both ends of the heat transfer plate in the second direction; and- a second projecting portion (23) formed on an outflow side of each of the heat transfer plates and configured to perform positioning in placing the inner fin (4, 5) into the heat transfer plate,- the first direction being a direction of flow of the fluid through the flow passage,- the second direction being a direction orthogonal to the first direction, and- the inner fin (4, 5) being disposed between the first projecting portion (22) and the second projecting portion (23).
- The plate-type heat exchanger (100) of claim 1,wherein the inner fin (4, 5) includes an offset fin having a corrugated portion formed in a corrugated shape by alternately coupling, in the second direction, vertical walls oriented perpendicularly to the heat transfer plate and horizontal walls oriented parallel to the heat transfer plate, andwherein a width of the first projecting portion (22) in the second direction is twice or more and five times or less as great at a distance between two adjacent ones of the vertical walls of the inner fin (4, 5).
- The plate-type heat exchanger (100) of claim 2,
wherein a width of the second projecting portion (23) in the second direction is twice or more and five times or less as great as the distance between the two adjacent vertical walls of the inner fin (4, 5). - The plate-type heat exchanger (100) of any one of claims 1 to 3,
wherein the second projecting portion (23) includes second projecting portions provided at both ends of the outflow side of the heat transfer plate in the second direction. - The plate-type heat exchanger (100) of claim 1 or 2,
wherein the first projecting portion (22) and the second projecting portion (23) are provided to project toward the flow passage from one of two of the heat transfer plates forming the flow passage. - The plate-type heat exchanger (100) of claim 5,
wherein the first projecting portion (22) and the second projecting portion (23) are joined to another one of the two heat transfer plates forming the flow passage. - The plate-type heat exchanger (100) of any one of claims 1 to 6,wherein the flow passage includes a first flow passage (6) and a second flow passage (7) alternately formed in a direction of stacking of the heat transfer plates, andwherein the first projecting portion (22) and the second projecting portion (23) include a first projecting portion and a second projecting portion provided in the first flow passage (6) and a first projecting portion and a second projecting portion provided in the second flow passage (7).
- The plate-type heat exchanger (100) of claim 7,wherein the direction of flow of the fluid through the first flow passage (6) and the direction of flow of the fluid through the second flow passage (7) are opposite to each other, andwherein the first projecting portion of the first flow passage (6) and the second projecting portion (7) of the second flow passage 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.
- The plate-type heat exchanger (100) of claim 7,wherein the direction of flow of the fluid through the first flow passage (6) and the direction of flow of the fluid through the second flow passage (7) are opposite to each other, andwherein the second projecting portion (23) of the first flow passage (6) and the first projecting portion (22) 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.
- The plate-type heat exchanger (100) of any one of claims 1 to 9,wherein each of the heat transfer plates has a flat portion (30) on which the inner fin (4, 5) is disposed,wherein the first projecting portion (22) includes first projecting portions provided at both ends of the flat portion (30) in the second direction and within an area surrounded by a first line representing an inflow edge of both edges of the inner fin (4, 5) in the first direction, two second lines representing both edges of the flat portion (30) in the second direction, and two circular arcs (28) at both ends of the flat portion (30) in the second direction,wherein each of the two circular arcs (28) 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, andwherein the radius R is three times as great as a flow passage height of the flow passage.
- The plate-type heat exchanger (100) of claim 10,wherein the second projecting portion (23) includes second projecting portions provided at both ends of the flat portion (30) in the second direction and within an area surrounded by a third line representing an outflow edge of both edges of the inner fin (4, 5) in the first direction, the two second lines, and two circular arcs (28) at both ends of the flat portion (30) in the second direction, wherein each of the two circular arcs (28) 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, andwherein the radius R is three times as great as a flow passage height of the flow passage.
- The plate-type heat exchanger (100) of any one of claims 1 to 7,wherein one of two of the heat transfer plates forming the flow passage is provided with the first second projecting portion (23) and the first projection portion (22) projecting toward the flow passage,wherein another one of the two heat transfer plates has a first depressed portion (40) and a second depressed portion (41) located opposite the first projecting portion and the second projection portion, depressed toward the flow passage, and formed in contact with the first second projecting portion (23) and the first projecting portion (22).
- The plate-type heat exchanger (100) of claim 12,
wherein points of contact between the first projecting portion (22) of one of the heat transfer plates and the second depressed portion (41) of the other one of the heat transfer plates and points of contact between the second projecting portion (23) of one of the heat transfer plates and the first depressed portion (40) of the other one of the heat transfer plates are joined. - The plate-type heat exchanger (100) of claim 12 or 13,wherein the flow passage includes a first flow passage (6) and a second flow passage (7) alternately formed in a direction of stacking of the heat transfer plates, the direction of flow of the fluid through the first flow passage (6) and the direction of flow of the fluid through the second flow passage (7) are opposite to each other,wherein the first projecting portion (22) of one of the heat transfer plates and the second projecting portion (23) of the other one of the heat transfer plates 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 plate-type heat exchanger (100) of claim 12 or 13,wherein the flow passage includes a first flow passage (6) and a second flow passage (7) alternately formed in a direction of stacking of the heat transfer plates, the direction of flow of the fluid through the first flow passage (6) and the direction of flow of the fluid through the second flow passage (7) are opposite to each other,wherein the second projecting portion (23) of one of the heat transfer plates and the first projecting portion (22) of the other one of the heat transfer plates 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 plate-type heat exchanger (100) of any one of claims 1 to 15,
wherein each of the heat transfer plates includes two plates partially joined to each other. - The plate-type heat exchanger (100) of any one of claims 1 to 16,wherein each of the heat transfer plates has header portions formed at both ends thereof in the first direction, andwherein each of the header portions (24) has a projecting and depressed structure (52) formed to bring about improvement in strength.
- The plate-type heat exchanger (100) of claim 17,wherein the projecting and depressed structure (52) has a plurality of circular depressed portions provided in one of two of the heat transfer plates forming the flow passage and a plurality of circular projecting portions (51) provided in another one of the two heat transfer plates to face the plurality of depressed portions (50),wherein each of the depressed portions (50) and a corresponding one of the projecting portions (51) are joined to each other,wherein the projecting and depressed structure (52) is not formed at least in areas extending over a distance δ from both ends of the inner fin (4, 5) in the first direction, andwherein the distance δ is equal to or greater than an equivalent diameter of a cross-sectional shape obtained by cutting a junction between the depressed portion and the projecting portion along a surface perpendicular to the first direction through a center of the junction.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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PCT/JP2018/042436 WO2020100276A1 (en) | 2018-11-16 | 2018-11-16 | Plate-type heat exchanger, heat pump device, and heat-pump-type cooling/heating hot-water supply system |
Publications (3)
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EP3882556A1 EP3882556A1 (en) | 2021-09-22 |
EP3882556A4 EP3882556A4 (en) | 2021-11-10 |
EP3882556B1 true EP3882556B1 (en) | 2023-10-11 |
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EP18940018.7A Active EP3882556B1 (en) | 2018-11-16 | 2018-11-16 | Plate-type heat exchanger, heat pump device, and heat-pump-type cooling/heating hot-water supply system |
Country Status (5)
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US (1) | US20210341186A1 (en) |
EP (1) | EP3882556B1 (en) |
JP (1) | JP6529709B1 (en) |
CN (1) | CN112997045B (en) |
WO (1) | WO2020100276A1 (en) |
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JP7247717B2 (en) * | 2019-04-01 | 2023-03-29 | 株式会社デンソー | Heat exchanger |
FR3122728B1 (en) * | 2021-05-06 | 2023-06-02 | Commissariat A L’Energie Atomique Et Aux Energies Alternatives | Channel plate heat exchanger module incorporating at least one fluid supply and distribution zone formed by studs. |
DE102022103720A1 (en) | 2022-02-17 | 2023-08-17 | Mahle International Gmbh | Heat exchanger with optimized pressure loss |
US20230400262A1 (en) * | 2022-06-13 | 2023-12-14 | Hamilton Sundstrand Corporation | Supercooled thermal storage for high load short duration cooling |
EP4343252A1 (en) * | 2022-09-20 | 2024-03-27 | Alfa Laval Corporate AB | A plate heat exchanger |
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2018
- 2018-11-16 JP JP2019514832A patent/JP6529709B1/en active Active
- 2018-11-16 WO PCT/JP2018/042436 patent/WO2020100276A1/en unknown
- 2018-11-16 US US17/281,989 patent/US20210341186A1/en active Pending
- 2018-11-16 EP EP18940018.7A patent/EP3882556B1/en active Active
- 2018-11-16 CN CN201880098848.9A patent/CN112997045B/en active Active
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US20210341186A1 (en) | 2021-11-04 |
JPWO2020100276A1 (en) | 2021-02-15 |
CN112997045A (en) | 2021-06-18 |
CN112997045B (en) | 2022-12-20 |
JP6529709B1 (en) | 2019-06-12 |
EP3882556A4 (en) | 2021-11-10 |
WO2020100276A1 (en) | 2020-05-22 |
EP3882556A1 (en) | 2021-09-22 |
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