US20140054017A1 - Heat exchange apparatus - Google Patents
Heat exchange apparatus Download PDFInfo
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- US20140054017A1 US20140054017A1 US14/114,655 US201214114655A US2014054017A1 US 20140054017 A1 US20140054017 A1 US 20140054017A1 US 201214114655 A US201214114655 A US 201214114655A US 2014054017 A1 US2014054017 A1 US 2014054017A1
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- Prior art keywords
- fins
- heat exchanger
- pitch
- heat transfer
- flow direction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
-
- 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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
- F28F1/128—Fins with openings, e.g. louvered fins
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2215/00—Fins
- F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
Definitions
- FIG. 2 is an enlarged perspective view of the main part of the heat exchanger shown in FIG. 1 .
- FIG. 10B is a cross-sectional view taken along the line D-D in FIG. 10A .
- a seventh aspect of the present disclosure provides the heat exchanger as set forth in any one of the second to fourth aspects, wherein the flat portions form a series of steps descending in a direction inclined with respect to the external flow direction and the internal flow direction. According to the seventh aspect, drainage of meltwater resulting from melting of frost can be facilitated.
- a tenth aspect of the present disclosure provides the heat exchanger as set forth in any one of the first to seventh aspects, wherein when an odd number of the fins are arranged in series from above in the internal flow direction, and odd-numbered fins are defined as first fins and even-numbered fins are defined as second fins, a total sum of the pitches between the first fins and the fins adjacent to and below the first fins is equal to a total sum of the pitches between the second fins and the fins adjacent to and below the second fins.
- the total sum of the areas of bonding between one of the two adjacent heat transfer tubes and the corrugated member is equal or almost equal to the total sum of the areas of bonding between the other one of the adjacent heat transfer tubes and the corrugated member. Therefore, the adjacent heat transfer tubes have the same or almost the same area for heat transfer to/from the corrugated member.
- a thirteenth aspect of the present disclosure provides the heat exchanger as set forth in any one of the first to twelfth aspects, wherein the adjacent heat transfer tubes are flat tubes that are parallel to each other.
- FIG. 1 shows a heat exchanger 1 according to the first embodiment of the present invention.
- This heat exchanger 1 exchanges heat between a refrigerant and air, and is used, for example, in a room air conditioner or a car air conditioner.
- a refrigerant a HFC refrigerant, a HC refrigerant, CO2, or the like can be used.
- the adjacent heat transfer tubes 3 are flat tubes that are parallel to each other, and have a cross-sectional shape extended in the Z direction.
- the corrugated member 4 is disposed between each pair of adjacent heat transfer tubes 3 .
- the first pitch P1 and the second pitch 2 are defined by the X-direction dimensions of the folded portions 6 that join the adjacent fins 5 .
- the folded portion 6 that is bonded to one of the two adjacent heat transfer tubes 3 (the left or central heat transfer tube 3 in FIG. 3A ) is elongated in the X direction compared to the folded portion 6 that is bonded to the other heat transfer tube 3 (the central or right heat transfer tube in FIG. 3A ). Therefore, the first pitch P1 and the second pitch P2 appear alternately. In other words, the air flow passage 42 exposed to one of the two adjacent heat transfer tubes 3 is narrower, while the air flow passage 41 exposed to the other heat transfer tube 3 is wider.
- the heat exchanger 1 has at least four (seven in FIG. 1 ) heat transfer tubes 3 .
- a pair of corrugated members 4 having the same shape are bonded to both sides of the heat transfer tube 3 (the central heat transfer tube 3 in FIG. 2 or FIG. 3A ) interposed between the two adjacent heat transfer tubes 3 in such a manner that these corrugated members 4 coincide with each other by parallel displacement in the Y direction. Therefore, in the heat transfer tubes 3 interposed between the two adjacent heat transfer tubes 3 (five heat transfer tubes 3 in FIG. 1 ), the total sums of the areas of bonding to the corrugated members 4 are equal or almost equal to each other. Thus, these heat transfer tubes 3 interposed between the two adjacent heat transfer tubes 3 have the same or almost the same area for heat transfer to/from the corrugated members 4 . Therefore, the refrigerant flowing in each of these heat transfer tubes 3 is uniformly heated by the air.
- the two corrugated members 4 having the same shape only have to be bonded to both sides of the heat transfer tube 3 interposed between the two adjacent heat transfer tubes 3 in such a manner that these corrugated members 4 coincide with each other by parallel displacement in an arbitrary direction.
- the two corrugated members 4 having the same shape may be bonded to both sides of the heat transfer tube 3 interposed between the two adjacent heat transfer tubes 3 in such a manner that these corrugated members 4 coincide with each other by parallel displacement in the X and Y directions.
- the two corrugated members 4 having the same shape may be bonded to both sides of the heat transfer tube 3 interposed between the two adjacent heat transfer tubes 3 in such a manner that these corrugated members 4 coincide with each other by parallel displacement in the Y and Z directions.
- the total sum of the pitches between the first fins and the fins adjacent to and below the first fins is equal to the total sum of the pitches of the second fins and the fins adjacent to and below the second fins.
- these total sums of the pitches are both 2 ⁇ P2+P1.
- the total sum of the areas of bonding between one of the two adjacent heat transfer tubes 3 and the corrugated member 4 is equal or almost equal to the total sum of the areas of bonding between the other heat transfer tube 3 and the corrugated member 4 in a range including positions corresponding to the odd number of fins 5 .
- the fins 5 do not necessarily have to be arranged at two different pitches, and they may be arranged at three or more different pitches.
- the smallest pitch may be regarded as the second pitch as defined in this embodiment, and the medium or largest pitch may be regarded as the first pitch as defined in this embodiment.
- the medium pitch may be regarded as the second pitch as defined in this embodiment, and the largest pitch may be regarded as the first pitch as defined this embodiment.
- the corrugated members 4 having the fins 5 that are arranged at irregular pitches do not have to be disposed between all pairs of heat transfer tubes 3 , and they may be disposed between at least one pair of adjacent heat transfer tubes 3 .
- the heat exchanger may be configured such that the corrugated member having the fins 5 that are arranged at a constant pitch is disposed between a pair of heat transfer tubes 3 in a region where the air flows at the highest rate in the heat exchanger (for example, the central region of the heat exchanger) and the corrugated members 4 having the fins 5 that are arranged at irregular pitches are disposed between the other pairs of heat transfer tubes 3 .
- the each of the fins 5 is composed of a plurality of flat portions that are arranged in a staggered manner in the Z direction.
- the plurality of flat portions are arranged in the Z direction so that slits opening in the Z direction are formed between the flat portions.
- the fin 5 undulates in the X direction, and is composed of first flat portions 51 and second flat portions 52 that are arranged in a staggered manner in the Z direction.
- the first flat portions 51 and the second flat portions 52 extend perpendicular to the X direction, and slits 53 opening in the Z direction are formed between them.
- the fins 5 are arranged at irregular pitches. Therefore, for example, even if frost forms on the outdoor heat exchanger during heating operation and the narrower air flow passages 42 are blocked, the wider air flow passages 41 are less likely to be blocked. Rather, when the narrower air flow passages 42 are blocked, the flow rate of the air increases in the wider air flow passages 41 , which makes the blockage thereof less likely to occur. Therefore, the heat exchanger can perform heat exchange between the refrigerant and the air continuously.
- the center of the fin 5 is located at the intermediate position between the upper flat portion 53 and the lower flat portion 55 and coincides with the center line of the middle flat portion 54 in its thickness direction.
- the fins 5 are arranged at irregular pitches (the first pitch P1 and the second pitch P2) in the X direction.
- the slits 58 are formed between the upper flat portions 53 and the middle flat portions 54 and between the middle flat portions 54 and the lower flat portions 55 . Therefore, according to this modification, the same effects as those of this embodiment can be exerted.
Abstract
Description
- The present invention relates to a heat exchanger that exchanges heat between a refrigerant and air.
- Conventionally, heat exchangers for exchanging heat between a refrigerant and air are used in air conditioners and the like. For example, Patent Literature 1 discloses a heat exchanger including flat tubes in which a refrigerant flows and corrugated members disposed between the flat tubes. The corrugated members each have flat portions arranged in a direction in which the flat tubes extend and raised portions arranged between the flat portions to join them, and form flow passages for allowing the air to flow therethrough.
- Patent Literature 1: JP 2004-317002 A
- SUMMARY OF INVENTION
- In the heat exchanger of Patent Literature 1, the flat portions are arranged at a constant pitch. Therefore, in the case where this heat exchanger is used as an outdoor heat exchanger for an air conditioner, if frost forms thereon during heating operation, the frost blocks all the air flow passages between the flat portions simultaneously, which may make it impossible to continue heat exchange between the refrigerant and air.
- Under these circumstances, it is an object of the present invention to provide a heat exchanger capable of performing heat exchange between a refrigerant and air continuously even if frost forms thereon.
- In order to solve the above problem, the heat exchanger of the present invention is a heat exchanger that exchanges heat between a refrigerant and air and includes: a plurality of heat transfer tubes extending in an internal flow direction in which the refrigerant flows; and a corrugated member having a corrugated shape. The corrugated member includes: a plurality of fins that are arranged at at least two different pitches, a relatively large first pitch and a relatively small second pitch, in the internal flow direction; and a plurality of folded portions that are bonded alternately in the internal flow direction to the heat transfer tubes that are adjacent to each other.
- In the configuration described above, the fins are arranged at irregular pitches. Therefore, for example, even if frost forms on the outdoor heat exchanger during heating operation and narrower air flow passages formed between the fins with a smaller pitch are blocked, wider air flow passages formed between the fins with a larger pitch are less likely to be blocked. Rather, when the narrower air flow passages formed between the fins with the smaller pitch are blocked, the flow rate of the air increases between the fins arranged at the larger pitch, which makes the blockage of the wider air flow passages less likely to occur. This is because the frost is removed from the air flow passages by the air flowing therein at a high flow rate before the frost grows thick enough. Therefore, the heat exchanger can perform heat exchange between the refrigerant and the air continuously.
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FIG. 1 is a front view of a heat exchanger according to a first embodiment of the present invention. -
FIG. 2 is an enlarged perspective view of the main part of the heat exchanger shown inFIG. 1 . -
FIG. 3A is an enlarged front view of the main part of the heat exchanger shown inFIG. 1 . -
FIG. 3B is a cross-sectional view taken along the line A-A inFIG. 3A . -
FIG. 4 is a diagram illustrating how the heat exchanger works when frost forms thereon. -
FIG. 5 is a perspective view of a corrugated member according to the first embodiment of the present invention. -
FIG. 6A is an enlarged front view of the main part of a heat exchanger according to a modification of the first embodiment of the present invention. -
FIG. 6B is a cross-sectional view taken along the line B-B inFIG. 6A . -
FIG. 7A is an enlarged front view of the main part of a heat exchanger according to a second embodiment of the present invention. -
FIG. 7B is a cross-sectional view taken along the line C-C inFIG. 7A . -
FIG. 8 is a perspective view of a corrugated member according to the second embodiment of the present invention. -
FIG. 9A is a diagram illustrating how the heat exchanger works when frost forms thereon. -
FIG. 9B is a diagram illustrating how the heat exchanger works on meltwater. -
FIG. 10A is an enlarged front view of the main part of a heat exchanger according to a modification of the second embodiment of the present invention. -
FIG. 10B is a cross-sectional view taken along the line D-D inFIG. 10A . -
FIG. 11 is a perspective view of a corrugated member according to a modification of the second embodiment. -
FIG. 12A is an enlarged front view of the main part of a heat exchanger according to another modification of the second embodiment. -
FIG. 12B is a cross-sectional view taken along the line E-E inFIG. 12A . -
FIG. 13 is a diagram illustrating how the heat exchanger works when frost forms thereon and how it works on meltwater. -
FIG. 14 is a perspective view of a corrugated member according to another modification of the second embodiment. - A first aspect of the present disclosure provides a heat exchanger that exchanges heat between a refrigerant and air, including: a plurality of heat transfer tubes extending in an internal flow direction in which the refrigerant flows; and a corrugated member having a corrugated shape. The corrugated member includes: a plurality of fins that are arranged at at least two different pitches, a relatively large first pitch and a relatively small second pitch, in the internal flow direction; and a plurality of folded portions that are bonded alternately in the internal flow direction to the heat transfer tubes that are adjacent to each other.
- A second aspect of the present disclosure provides the heat exchanger as set forth in the first aspect, wherein each of the fins includes a plurality of flat portions that are arranged in a staggered or stepped manner in an external flow direction perpendicular to the internal flow direction and a direction in which the heat transfer tubes are arranged, and slits opening in the external flow direction are formed between the flat portions. According to the second aspect, water resulting from melting of frost runs down through the slits formed between the flat portions. Therefore, the water is well drained.
- A third aspect of the present disclosure provides the heat exchanger as set forth in the second aspect, wherein the fins are arranged in such a manner that the fins coincide with each other by parallel displacement in the internal flow direction. According to the third aspect, between the two adjacent fins, the flat portions of one of the fins and the counterpart flat portions of the other fin face each other in the internal flow direction such that the distance between these facing flat portions in the internal direction is kept constant at any position in the external flow direction. In addition, since the air is likely to flow at a constant rate in the air passage, a less turbulent air flow can be formed. Furthermore, such a corrugated member can be produced easily.
- A fourth aspect of the present disclosure provides the heat exchanger as set forth in the second aspect or the third aspect, wherein widths of the flat portions are equal in the external flow direction. According to the fourth aspect, the ratio between the surface area and the volume of each of the flat portions is constant. Therefore, the heat transfer efficiency of the fins is optimized.
- A fifth aspect of the present disclosure provides the heat exchanger as set forth in any one of the second to fourth aspects, wherein the flat portions are first flat portions and second flat portions that are arranged in a staggered manner in the external flow direction. According to the fifth aspect, a relatively large slit can be formed between the first flat portion and the second flat portion. In addition, an air flow passage extending straight in the external flow direction can be formed. Furthermore, since the upper and lower edges of the fins are in direct contact with the heat transfer tubes, these fins can achieve a higher fin efficiency than louvered fins and the like.
- A sixth aspect of the present disclosure provides the heat exchanger as set forth in the fifth aspect, wherein the slits are formed between the first flat portions and the second flat portions, and a dimension of each of the slits in the internal flow direction is one half or less of the second pitch. According to the sixth aspect, the largest possible air passages can be obtained.
- A seventh aspect of the present disclosure provides the heat exchanger as set forth in any one of the second to fourth aspects, wherein the flat portions form a series of steps descending in a direction inclined with respect to the external flow direction and the internal flow direction. According to the seventh aspect, drainage of meltwater resulting from melting of frost can be facilitated.
- An eighth aspect of the present disclosure provides the heat exchanger as set forth in any one of the first to seventh aspects, wherein the fins are arranged so that the second pitch appears before and after the first pitch. According to the eighth aspect, spread of frost in the internal flow direction can be inhibited.
- A ninth aspect of the present disclosure provides the heat exchanger as set forth in any one of the first to seventh aspects, wherein the first pitch and the second pitch appear alternately. According to the ninth aspect, spread of frost in the internal flow direction can be inhibited.
- A tenth aspect of the present disclosure provides the heat exchanger as set forth in any one of the first to seventh aspects, wherein when an odd number of the fins are arranged in series from above in the internal flow direction, and odd-numbered fins are defined as first fins and even-numbered fins are defined as second fins, a total sum of the pitches between the first fins and the fins adjacent to and below the first fins is equal to a total sum of the pitches between the second fins and the fins adjacent to and below the second fins. According to the tenth aspect, the total sum of the areas of bonding between one of the two adjacent heat transfer tubes and the corrugated member is equal or almost equal to the total sum of the areas of bonding between the other one of the adjacent heat transfer tubes and the corrugated member. Therefore, the adjacent heat transfer tubes have the same or almost the same area for heat transfer to/from the corrugated member.
- An eleventh aspect of the present disclosure provides the heat exchanger as set forth in any one of the first to tenth aspects, wherein the first pitch is 1.2 times or more and 3.0 times or less the second pitch. According to the eleventh aspect, it is possible to allow the corrugated member to have a sufficiently large heat transfer area as a whole while inhibiting blockage of the air flow passages due to frost formation.
- A twelfth aspect of the present disclosure provides the heat exchanger as set forth in any one of the first to eleventh aspects, wherein the plurality of heat transfer tubes includes at least four of the heat transfer tubes, and a pair of the corrugated members having the same shape are bonded to both sides of each of the heat transfer tubes interposed between the two adjacent heat transfer tubes in such a manner that the corrugated members coincide with each other by parallel displacement in an arbitrary direction. According to the twelfth aspect, in the heat transfer tubes interposed between the two adjacent heat transfer tubes, the total sums of the areas of bonding to the corrugated members are equal or almost equal to each other. Therefore, these heat transfer tubes have the same or almost the same area for heat transfer to/from the corrugated members.
- A thirteenth aspect of the present disclosure provides the heat exchanger as set forth in any one of the first to twelfth aspects, wherein the adjacent heat transfer tubes are flat tubes that are parallel to each other.
- Hereinafter, embodiments of the present invention will be described with reference to the drawings. It should be noted that the following description of the present invention is merely exemplary and is not intended to limit the present invention.
-
FIG. 1 shows a heat exchanger 1 according to the first embodiment of the present invention. This heat exchanger 1 exchanges heat between a refrigerant and air, and is used, for example, in a room air conditioner or a car air conditioner. As the refrigerant, a HFC refrigerant, a HC refrigerant, CO2, or the like can be used. - Specifically, the heat exchanger 1 includes a plurality of
heat transfer tubes 3 in which the refrigerant flows and a pair ofheaders 2 to which both ends of each of theheat transfer tubes 3 are connected. Theheat transfer tubes 3 extend in a specific direction, and are arranged in a direction perpendicular to the specific direction. Here, the refrigerant flows in the specific direction in theheat transfer tubes 3. The pair ofheaders 2 extend in the arrangement direction of theheat transfer tubes 3. Hereinafter, in order to simplify the description, the specific direction (an internal flow direction of the present invention), the arrangement direction of theheat transfer tubes 3, and the direction perpendicular to these directions (an external flow direction of the present invention) are referred to as an X direction, a Y direction, and a Z direction, respectively. - In this embodiment, the Y direction and the Z direction are the horizontal directions, and the X direction is the vertical direction. In other words, the pair of
headers 2 extend in the horizontal direction, and theheat transfer tubes 3 disposed between theheaders 2 extend in the vertical direction. Theheat transfer tubes 3 do not necessarily have to extend in the vertical direction, and may extend in an oblique direction or in the horizontal direction. The pair ofheaders 2 do not necessarily have to extend in the horizontal direction, and may extend in the vertical direction. - As shown in
FIG. 2 , the adjacentheat transfer tubes 3 are flat tubes that are parallel to each other, and have a cross-sectional shape extended in the Z direction. Thecorrugated member 4 is disposed between each pair of adjacentheat transfer tubes 3. - As shown in
FIG. 3A andFIG. 3B , thecorrugated member 4 has a corrugatedshape including fins 5 that are arranged in the X direction and foldedportions 6 that are bonded alternatively to the adjacentheat transfer tubes 3. That is, the foldedportions 6 are bonded alternately in the X direction to the adjacentheat transfer tubes 3. Thus,air flow passages heat transfer tubes 3 and extending in the Z direction are formed between thefins 5. In this embodiment, as shown inFIG. 5 , thefins 5 have a straight shape extending in the Z direction. In other words, thefins 5 have a flat shape extending in the Y and Z directions. - The
fins 5 are arranged at at least two different pitches, a relatively large first pitch P1 and a relatively small second pitch P2, in the X direction. As shown inFIG. 3A andFIG. 3B , in this embodiment, thefins 5 are arranged so that the second pitch P2 appears before and after the first pitch P1. The term “pitch” refers to the center-to-center distance between theadjacent fins 5, and in this embodiment, the center of thefin 5 refers to the center line of the flat-shapedfin 5 in its thickness direction (X direction). - The first pitch P1 and the
second pitch 2 are defined by the X-direction dimensions of the foldedportions 6 that join theadjacent fins 5. In this embodiment, as shown inFIG. 3A , the foldedportion 6 that is bonded to one of the two adjacent heat transfer tubes 3 (the left or centralheat transfer tube 3 inFIG. 3A ) is elongated in the X direction compared to the foldedportion 6 that is bonded to the other heat transfer tube 3 (the central or right heat transfer tube inFIG. 3A ). Therefore, the first pitch P1 and the second pitch P2 appear alternately. In other words, theair flow passage 42 exposed to one of the two adjacentheat transfer tubes 3 is narrower, while theair flow passage 41 exposed to the otherheat transfer tube 3 is wider. - In the heat exchanger 1 of this embodiment, the
fins 5 are arranged at irregular pitches. Therefore, as shown inFIG. 4 , for example, even if frost forms on the outdoor heat exchanger during heating operation and the narrowerair flow passages 42 are blocked, the widerair flow passages 41 are less likely to be blocked. Rather, when the narrowerair flow passages 42 are blocked, the flow rate of the air increases in the widerair flow passages 41, which makes the blockage thereof less likely to occur. Therefore, the heat exchanger can perform heat exchange between the refrigerant and the air continuously. - Preferably, the first pitch P1 is 1.2 times or more and 3.0 times or less the second pitch P2. When the ratio P1/P2 is 1.2 or more, the likelihood of blockage of the wider
air flow passages 41 due to frost formation can be reduced sufficiently. When the ratio of P1/P2 is 3.0 or less, thecorrugated members 4 are allowed to have a sufficiently large heat transfer area as a whole. In view of these, it is preferable that the ratio P1/P2 satisfy 1.5≦P1/P2≦1.8. - As shown in
FIG. 1 , the heat exchanger 1 has at least four (seven inFIG. 1 )heat transfer tubes 3. As shown inFIG. 2 orFIG. 3A , a pair ofcorrugated members 4 having the same shape are bonded to both sides of the heat transfer tube 3 (the centralheat transfer tube 3 inFIG. 2 orFIG. 3A ) interposed between the two adjacentheat transfer tubes 3 in such a manner that thesecorrugated members 4 coincide with each other by parallel displacement in the Y direction. Therefore, in theheat transfer tubes 3 interposed between the two adjacent heat transfer tubes 3 (fiveheat transfer tubes 3 inFIG. 1 ), the total sums of the areas of bonding to thecorrugated members 4 are equal or almost equal to each other. Thus, theseheat transfer tubes 3 interposed between the two adjacentheat transfer tubes 3 have the same or almost the same area for heat transfer to/from thecorrugated members 4. Therefore, the refrigerant flowing in each of theseheat transfer tubes 3 is uniformly heated by the air. - The two
corrugated members 4 having the same shape only have to be bonded to both sides of theheat transfer tube 3 interposed between the two adjacentheat transfer tubes 3 in such a manner that thesecorrugated members 4 coincide with each other by parallel displacement in an arbitrary direction. For example, the twocorrugated members 4 having the same shape may be bonded to both sides of theheat transfer tube 3 interposed between the two adjacentheat transfer tubes 3 in such a manner that thesecorrugated members 4 coincide with each other by parallel displacement in the X and Y directions. Instead, the twocorrugated members 4 having the same shape may be bonded to both sides of theheat transfer tube 3 interposed between the two adjacentheat transfer tubes 3 in such a manner that thesecorrugated members 4 coincide with each other by parallel displacement in the Y and Z directions. Furthermore, the twocorrugated members 4 having the same shape may be bonded to both sides of theheat transfer tube 3 interposed between the two adjacentheat transfer tubes 3 in such a manner that thesecorrugated members 4 coincide with each other by parallel displacement in the X, Y and Z directions. In any of these configurations, theheat transfer tubes 3 interposed between the two adjacentheat transfer tubes 3 have the same or almost the same area for heat transfer to/from thecorrugated members 4. Therefore, the refrigerant flowing in each of theheat transfer tubes 3 is uniformly heated by the air. - The heat exchanger 1 of the first embodiment can be modified from various points of view. For example, each of the
fins 5 may be provided with louvers that are inclined with respect to thefin 5 and arranged in the Z direction. - The
fins 5 do not have to be arranged so that the second pitch P2 appears before and after the first pitch P1. In order to inhibit blockage of the air flow passages when frost forms, thefins 5 have to be arranged so that at least one first pitch P1 appears. - The first pitch P1 and the second pitch P2 do not necessarily have to appear alternately. A series of the second pitches may appear either before or after the first pitch or before and after the first pitch. For example, the
fins 5 may be arranged as shown inFIG. 6A andFIG. 6B . When it is assumed that an odd number of (seven inFIG. 6B )fins 5 are arranged in series from above in the X direction, the odd-numberedfins 5 are defined as first fins and the even-numberedfins 5 are defined as second fins. In this case, as shown inFIG. 6B , for these odd-numberedfins 5, the total sum of the pitches between the first fins and the fins adjacent to and below the first fins is equal to the total sum of the pitches of the second fins and the fins adjacent to and below the second fins. InFIG. 6B , these total sums of the pitches are both 2×P2+P1. In this configuration, the total sum of the areas of bonding between one of the two adjacentheat transfer tubes 3 and thecorrugated member 4 is equal or almost equal to the total sum of the areas of bonding between the otherheat transfer tube 3 and thecorrugated member 4 in a range including positions corresponding to the odd number offins 5. Thus, theheat transfer tubes 3 have the same or almost the same area for heat transfer to/from thecorrugated member 4. Therefore, the refrigerant flowing in each of theheat transfer tubes 3 is uniformly heated by the air. In this case, it is preferable that thefins 5 be formed so that the above relation is satisfied in the entirecorrugated member 4. However, thefins 5 may be formed so that the above relation is satisfied in a part of thecorrugated member 4. - The
fins 5 do not necessarily have to be arranged at two different pitches, and they may be arranged at three or more different pitches. For example, in the case where thefins 5 are arranged at three different pitches, the smallest pitch may be regarded as the second pitch as defined in this embodiment, and the medium or largest pitch may be regarded as the first pitch as defined in this embodiment. Instead, the medium pitch may be regarded as the second pitch as defined in this embodiment, and the largest pitch may be regarded as the first pitch as defined this embodiment. - The
corrugated members 4 having thefins 5 that are arranged at irregular pitches do not have to be disposed between all pairs ofheat transfer tubes 3, and they may be disposed between at least one pair of adjacentheat transfer tubes 3. For example, the heat exchanger may be configured such that the corrugated member having thefins 5 that are arranged at a constant pitch is disposed between a pair ofheat transfer tubes 3 in a region where the air flows at the highest rate in the heat exchanger (for example, the central region of the heat exchanger) and thecorrugated members 4 having thefins 5 that are arranged at irregular pitches are disposed between the other pairs ofheat transfer tubes 3. - Next, a second embodiment of the present invention is described. The second embodiment can be configured in the same manner as in the first embodiment, unless otherwise stated. The same or corresponding components are denoted by the same reference numerals as in the first embodiment, and the description thereof may be omitted.
- As shown in
FIG. 7A andFIG. 7B , the each of thefins 5 is composed of a plurality of flat portions that are arranged in a staggered manner in the Z direction. In other words, the plurality of flat portions are arranged in the Z direction so that slits opening in the Z direction are formed between the flat portions. Specifically, thefin 5 undulates in the X direction, and is composed of firstflat portions 51 and secondflat portions 52 that are arranged in a staggered manner in the Z direction. The firstflat portions 51 and the secondflat portions 52 extend perpendicular to the X direction, and slits 53 opening in the Z direction are formed between them. Thefins 5 are arranged in such a manner that thefins 5 coincide with each other by parallel displacement in the X direction. Therefore, between the twoadjacent fins 5, the first and secondflat portions flat portions flat portions 51 and the distance between the facing secondflat portions 52 are kept constant at any position in the Z direction. It is preferable that the width of the firstflat portion 51 is equal to that of the secondflat portion 52 in the Z direction. - As shown in
FIG. 7A andFIG. 7B , thefins 5 are arranged at two different pitches, the first pitch P1 and the second pitch P2, in the X direction. In this embodiment, the center of thefin 5 is the reference line of the undulations of thefin 5 located at the midpoint between the firstflat portions 51 and the secondflat portions 52 of thefin 5. - The
corrugated member 4 configured as described above can be produced by making cuts in a flat metal plate (for example, an aluminum plate) to form the firstflat portions 51 and the secondflat portions 52 and then pressing the metal plate into shape or passing the metal plate through a pair of transfer rollers. In thecorrugated member 4 produced in this manner, the thickness of the firstflat portions 51 and the secondflat portions 52 is almost equal to the thickness of the foldedportions 6. - Also in this embodiment, the
fins 5 are arranged at irregular pitches. Therefore, for example, even if frost forms on the outdoor heat exchanger during heating operation and the narrowerair flow passages 42 are blocked, the widerair flow passages 41 are less likely to be blocked. Rather, when the narrowerair flow passages 42 are blocked, the flow rate of the air increases in the widerair flow passages 41, which makes the blockage thereof less likely to occur. Therefore, the heat exchanger can perform heat exchange between the refrigerant and the air continuously. - In addition, in this embodiment, each of the
fins 5 is composed of the firstflat portions 51 and the secondflat portions 52, and theslits 53 are formed between them. Therefore, as shown inFIG. 9A , even if the inlet side of the narrowerair flow passages 42 is blocked by frost, the air can be introduced into the narrowerair flow passages 42 through theslits 53 on the downstream side of thepassages 42. As a result, a decrease in the heating capacity can be suppressed. Furthermore, during defrosting operation for melting the frost, meltwater resulting from the melting of the frost runs down through theslits 53, as shown inFIG. 9B . Therefore, the water is well drained. In addition, the staggered arrangement of the firstflat portions 51 and the secondflat portions 52 in the Z direction creates straight air flows in the Z direction through theslits 53. These straight air flows push the meltwater resulting from the melting of the frost out in the Z direction. - From the viewpoint of maximizing the area of the narrower
air flow passages 42, the X-direction dimension L of theslit 53 formed between the firstflat portion 51 and the second flat portion 52 (seeFIG. 7B ) is preferably one half or less of the second pitch P2. Preferably, the dimension L is at least as large as the thickness of the firstflat portion 51 or at least as large as the thickness of the secondflat portion 52. For example, the X-direction dimension L of theslit 53 may be equal to the shortest distance between the firstflat portions 51 or the secondflat portions 52 of thefins 5 joined by the foldedportion 6 that defines the second pitch P2. - The heat exchanger 1 of the second embodiment can be modified from various points of view. For example, it can be modified based on the viewpoint described as the modification in the first embodiment.
- In each of the fins, the plurality of flat portions may be arranged in the form of at least two steps in the Z direction. For example, as shown in
FIG. 10A ,FIG. 10B , andFIG. 11 , each of thefins 5 may be composed of three different flat portions, upperflat portions 55, middleflat portions 56, and lowerflat portions 57. The upperflat portion 55 forms the top of the steps. The lowerflat portion 57 forms the bottom of the steps. The middleflat portion 56 is formed at an intermediate position between the upperflat portion 55 and the lowerflat portion 57.Slits 58 opening in the Z direction are formed between the upperflat portions 55 and the middleflat portions 56 and between the middleflat portions 56 and the lowerflat portions 57. The upperflat portions 55, the middleflat portions 56, and the lowerflat portions 57 are arranged in the Z direction so that ascending portions and descending portions appear alternately. However, they do not necessarily have to be arranged in this order. - In this modification, the center of the
fin 5 is located at the intermediate position between the upperflat portion 53 and the lowerflat portion 55 and coincides with the center line of the middle flat portion 54 in its thickness direction. Also in this modification, as shown inFIG. 10B , thefins 5 are arranged at irregular pitches (the first pitch P1 and the second pitch P2) in the X direction. Theslits 58 are formed between the upperflat portions 53 and the middle flat portions 54 and between the middle flat portions 54 and the lowerflat portions 55. Therefore, according to this modification, the same effects as those of this embodiment can be exerted. - Furthermore, as shown in
FIG. 12A ,FIG. 12B , andFIG. 14 , the plurality of flat portions of each of thefins 5 may form a series of steps descending in a direction inclined with respect to the Z direction and the X direction. As shown inFIG. 12B , in each of thefins 5, the plurality offlat portions 51A to 51F (six flat portions in this figure) are arranged in the form of steps descending from the inlet side of theair flow passages Slits 53A opening in the Z direction are formed between the adjacentflat portions 51A to 51F. - In this modification, the center of the
fin 5 is the reference line located at the midpoint between theflat portion 51A disposed on the inlet side of theair flow passage flat portion 51F disposed on the outlet side of theair flow passage FIG. 12B , thefins 5 are arranged at irregular pitches (the first pitch P1 and the second pitch P2) in the X direction. Theslits 53A are formed between the adjacentflat portions 51A to 51F. Therefore, according to this modification, the same effects as those of this embodiment can be exerted. Furthermore, as shown inFIG. 13 , water resulting from melting of frost during defrosting operation is pushed by the air flowing in theair flow passages air flow passages flat portions 51A to 51F. Therefore, according to this modification, drainage of water resulting from melting of frost can be facilitated.
Claims (13)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2011-229764 | 2011-10-19 | ||
JP2011229764 | 2011-10-19 | ||
PCT/JP2012/006689 WO2013057953A1 (en) | 2011-10-19 | 2012-10-18 | Heat exchange apparatus |
Publications (1)
Publication Number | Publication Date |
---|---|
US20140054017A1 true US20140054017A1 (en) | 2014-02-27 |
Family
ID=48140614
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/114,655 Abandoned US20140054017A1 (en) | 2011-10-19 | 2012-10-18 | Heat exchange apparatus |
Country Status (5)
Country | Link |
---|---|
US (1) | US20140054017A1 (en) |
EP (1) | EP2770289A4 (en) |
JP (1) | JP5967588B2 (en) |
CN (1) | CN103502765A (en) |
WO (1) | WO2013057953A1 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
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US20160313070A1 (en) * | 2014-02-10 | 2016-10-27 | Mitsubishi Heavy Industries Automotive Thermal Systems Co., Ltd. | Heat-exchanger offset fin and refrigerant heat-exchanger utilizing same |
CN107906648A (en) * | 2017-12-06 | 2018-04-13 | 广东美的制冷设备有限公司 | Radiation recuperator, indoor apparatus of air conditioner and air conditioner |
US10578370B2 (en) * | 2017-06-13 | 2020-03-03 | Modine Manufacturing Company | Integrated heat exchanger and coolant reservoir |
US11499210B2 (en) * | 2016-12-21 | 2022-11-15 | Mitsubishi Electric Corporation | Heat exchanger and method of manufacturing thereof, and refrigeration cycle apparatus |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN106643263B (en) * | 2015-07-29 | 2019-02-15 | 丹佛斯微通道换热器(嘉兴)有限公司 | Fin component for heat exchanger and the heat exchanger with the fin component |
JP2019219074A (en) * | 2018-06-15 | 2019-12-26 | 東芝ライフスタイル株式会社 | refrigerator |
CN111380394B (en) * | 2018-12-29 | 2022-02-01 | 杭州三花微通道换热器有限公司 | Heat exchanger |
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- 2012-10-18 CN CN201280021250.2A patent/CN103502765A/en active Pending
- 2012-10-18 EP EP12841386.1A patent/EP2770289A4/en not_active Withdrawn
- 2012-10-18 JP JP2013539538A patent/JP5967588B2/en active Active
- 2012-10-18 WO PCT/JP2012/006689 patent/WO2013057953A1/en active Application Filing
- 2012-10-18 US US14/114,655 patent/US20140054017A1/en not_active Abandoned
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US20160313070A1 (en) * | 2014-02-10 | 2016-10-27 | Mitsubishi Heavy Industries Automotive Thermal Systems Co., Ltd. | Heat-exchanger offset fin and refrigerant heat-exchanger utilizing same |
US11499210B2 (en) * | 2016-12-21 | 2022-11-15 | Mitsubishi Electric Corporation | Heat exchanger and method of manufacturing thereof, and refrigeration cycle apparatus |
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US10578370B2 (en) * | 2017-06-13 | 2020-03-03 | Modine Manufacturing Company | Integrated heat exchanger and coolant reservoir |
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Also Published As
Publication number | Publication date |
---|---|
CN103502765A (en) | 2014-01-08 |
WO2013057953A1 (en) | 2013-04-25 |
JPWO2013057953A1 (en) | 2015-04-02 |
EP2770289A4 (en) | 2015-03-04 |
EP2770289A1 (en) | 2014-08-27 |
JP5967588B2 (en) | 2016-08-10 |
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