WO2012098915A1 - Échangeur de chaleur et climatiseur - Google Patents

Échangeur de chaleur et climatiseur Download PDF

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Publication number
WO2012098915A1
WO2012098915A1 PCT/JP2012/000382 JP2012000382W WO2012098915A1 WO 2012098915 A1 WO2012098915 A1 WO 2012098915A1 JP 2012000382 W JP2012000382 W JP 2012000382W WO 2012098915 A1 WO2012098915 A1 WO 2012098915A1
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WO
WIPO (PCT)
Prior art keywords
flat tube
heat exchanger
edge
fins
tube
Prior art date
Application number
PCT/JP2012/000382
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English (en)
Japanese (ja)
Inventor
正憲 神藤
好男 織谷
圭史 芦田
Original Assignee
ダイキン工業株式会社
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Filing date
Publication date
Application filed by ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Publication of WO2012098915A1 publication Critical patent/WO2012098915A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28F1/24—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 and extending transversely
    • F28F1/32—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 and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • F28F2215/12—Fins with U-shaped slots for laterally inserting conduits

Definitions

  • the present invention relates to a heat exchanger that includes a flat tube and fins and exchanges heat between fluid flowing in the flat tube and air, and an air conditioner including the heat exchanger.
  • heat exchangers with flat tubes and fins are known.
  • a heat exchanger described in Patent Document 1 a plurality of flat tubes extending in the left-right direction are arranged one above the other at a predetermined interval, and plate-like fins are arranged at a predetermined interval from each other. They are arranged in the extending direction.
  • the flat tubes are inserted into fins and joined by brazing.
  • the air flowing between the fins exchanges heat with the fluid flowing in the flat tube.
  • the present invention has been made in view of such points, and an object thereof is to avoid a state in which fins come into contact with each other via a brazing material when the flat tube and the fin are joined by brazing.
  • 1st invention is formed in the plate shape extended in the sequence direction of the several flat tube (33) arranged up and down so that a side surface (33a) may oppose, and this flat tube (33),
  • Each said flat tube (33) is premised on a heat exchanger provided with a plurality of fins (36) having notches (45) which are inserted in an orthogonal direction and joined by brazing.
  • the edge part (46a, 46b) to which the said flat tube (33) of the said notch part (45) is joined is the state in which the said flat pipe (33) was inserted in the said notch part (45). It is bent so that a substantially V-shaped groove (60) is formed between the edge (46a, 46b) and the flat tube (33).
  • the edge portions (46a, 46b) to which the flat tube (33) of the notch portion (45) is joined are formed in a substantially square shape. Then, in a state where the flat tube (33) is inserted into the notch (45), a substantially V-shaped groove (60) is formed between the flat tube (33) and the edges (46a, 46b). Formed (see FIG. 7). In other words, the groove (60) becomes narrower toward the bottom.
  • the flat tube (33) and the notch (45) are brazed, the flat tube (33) is joined to the edges (46a, 46b) of the notch (45). The molten brazing material actively flows into the groove (60) by capillary action.
  • the entire circumference of the edge (46a, 46b) to which the flat tube (33) of the notch portion (45) is joined is the flat tube (33). Bent so that a substantially V-shaped groove (60) is formed between the edge (46a, 46b) and the flat tube (33) in a state of being inserted into the notch (45). It is what has been.
  • the groove (60) is formed on the entire circumference of the edge (46a, 46b) to which the flat tube (33) of the notch (45) is joined. Therefore, the amount of brazing material that flows into the groove (60) during joining by brazing increases. This further suppresses the amount of brazing material that flows between the fins (36).
  • an end of the flat tube (33) in the insertion direction into the notch (45) is continuous with the side surface (33a) and protrudes outward. It is a circular arc surface (33b).
  • the edge part to which the said flat tube (33) of the said notch part (45) is joined is the linear edge part (46a) corresponding to the side surface (33a) of the said flat pipe (33), and this linear form.
  • An arcuate edge portion (46b) that is continuous with the edge portion (46a) and corresponds to the arcuate surface (33b) of the flat tube (33) is provided.
  • the edge of the notch (45) has a shape corresponding to the shape of the flat tube (33), particularly the arc surface (33b) of the flat tube (33). A large contact area between (33) and the notch (45) can be earned.
  • the bending height of the linear edge (46a) is greater than the bending height of the arcuate edge (46b).
  • the bending height of the linear edge portion (46a) is the arcuate edge portion (46b). ) Is larger (higher) than the folding height of the arc-shaped edge (46b) when the edges (46a, 46b) are bent.
  • a fifth invention is directed to an air conditioner (10), and includes a refrigerant circuit (20) provided with the heat exchanger (30) of any one of the first to fourth inventions, and the refrigerant circuit In (20), the refrigerant is circulated to perform the refrigeration cycle.
  • the heat exchanger (30) of any one of the first to fourth aspects is connected to the refrigerant circuit (20).
  • the refrigerant circulating in the refrigerant circuit (20) flows through the flat tube (33) and exchanges heat with the air flowing around the flat tube (33).
  • the substantially V-shaped groove (60) can be formed between the flat tube (33) and the edge (46a, 46b).
  • the brazing material can be actively flowed into the groove (60) by capillary action. Therefore, a sufficient amount of brazing material can be secured at the joint between the flat tube (33) and the notch (45), and the amount of brazing material flowing between the fins (36) can be reduced accordingly. it can.
  • the state which fins (36) contact via a brazing material can be avoided. Therefore, increase in ventilation resistance between the fins (36) can be prevented, and as a result, it is possible to prevent the heat exchange efficiency of the heat exchanger (30) from decreasing.
  • the groove (60) can be formed on the entire periphery of the edge (46a, 46b) to which the flat tube (33) of the notch (45) is joined. Therefore, the amount of brazing material flowing into the groove (60) can be increased, and thereby the amount of brazing material flowing between the fins (36) can be further suppressed.
  • the shape of the edge (46a, 46b) of the notch (45) is made to correspond to the shape of the flat tube (33). You can earn a lot of contact area with the notch (45). Therefore, the amount of heat transfer between the flat tube (33) and the fin (36) can be earned sufficiently.
  • the folding height of the linear edge (46a) is made larger than the folding height of the arcuate edge (46b). It is possible to prevent the arcuate edge (46b) from being broken during processing. Therefore, the substantially V-shaped groove (60) can be appropriately and reliably formed between the flat tube (33) and the edges (46a, 46b). Therefore, at the time of joining by brazing, the amount of brazing material that flows between the fins (36) can be reliably suppressed.
  • FIG. 1 is a refrigerant circuit figure showing a schematic structure of an air harmony machine of an embodiment.
  • FIG. 2 is a schematic perspective view of the heat exchanger according to the embodiment.
  • Drawing 3 is a partial sectional view showing the front of the heat exchanger of an embodiment.
  • FIG. 4 is a cross-sectional view of the heat exchanger showing a part of the AA cross section of FIG. 5A and 5B are views showing the main parts of the fins of the heat exchanger according to the embodiment, wherein FIG. 5A is a front view and FIG. 5B is a cross-sectional view showing a BB cross section of FIG.
  • FIG. 6 is a cross-sectional view of the fin showing the CC cross section of FIG.
  • FIG. 7 is a schematic cross-sectional view showing the relationship between the flat tube and the tube insertion portion of the embodiment as viewed from the windward side.
  • the heat exchanger (30) of the present embodiment constitutes an outdoor heat exchanger (23) of the air conditioner (10). Then, the air conditioner (10) provided with the heat exchanger (30) of this embodiment is demonstrated, referring FIG.
  • the air conditioner (10) includes an outdoor unit (11) and an indoor unit (12).
  • the outdoor unit (11) and the indoor unit (12) are connected via a liquid side connecting pipe (13) and a gas side connecting pipe (14).
  • a refrigerant circuit (20) is formed by the outdoor unit (11), the indoor unit (12), the liquid side connecting pipe (13), and the gas side connecting pipe (14).
  • the refrigerant circuit (20) includes a compressor (21), a four-way switching valve (22), an outdoor heat exchanger (23), an expansion valve (24), and an indoor heat exchanger (25). .
  • the compressor (21), the four-way switching valve (22), the outdoor heat exchanger (23), and the expansion valve (24) are accommodated in the outdoor unit (11).
  • the outdoor unit (11) is provided with an outdoor fan (15) for supplying outdoor air to the outdoor heat exchanger (23).
  • the indoor heat exchanger (25) is accommodated in the indoor unit (12).
  • the indoor unit (12) is provided with an indoor fan (16) for supplying room air to the indoor heat exchanger (25).
  • the compressor (21) has its discharge side connected to the first port of the four-way switching valve (22) and its suction side connected to the second port of the four-way switching valve (22).
  • the outdoor heat exchanger (23), the expansion valve (24), and the indoor heat exchanger are sequentially arranged from the third port to the fourth port of the four-way switching valve (22). (25) and are arranged.
  • Compressor (21) is a scroll type or rotary type hermetic compressor.
  • the four-way switching valve (22) has a first state (state indicated by a broken line in FIG. 1) in which the first port communicates with the third port and the second port communicates with the fourth port, The port is switched to a second state (state indicated by a solid line in FIG. 1) in which the port communicates with the fourth port and the second port communicates with the third port.
  • the expansion valve (24) is a so-called electronic expansion valve.
  • the outdoor heat exchanger (23) exchanges heat between the outdoor air and the refrigerant.
  • the outdoor heat exchanger (23) is configured by the heat exchanger (30) of the present embodiment.
  • the indoor heat exchanger (25) exchanges heat between the indoor air and the refrigerant.
  • the indoor heat exchanger (25) is constituted by a so-called cross fin (36) type fin (36) and tube heat exchanger provided with a heat transfer tube which is a circular tube.
  • the air conditioner (10) performs a cooling operation.
  • the four-way switching valve (22) is set to the first state.
  • the outdoor fan (15) and the indoor fan (16) are operated.
  • Refrigeration cycle is performed in the refrigerant circuit (20). Specifically, the refrigerant discharged from the compressor (21) flows into the outdoor heat exchanger (23) through the four-way switching valve (22), dissipates heat to the outdoor air, and is condensed. The refrigerant flowing out of the outdoor heat exchanger (23) expands when passing through the expansion valve (24), then flows into the indoor heat exchanger (25), absorbs heat from the indoor air, and evaporates. The refrigerant that has flowed out of the indoor heat exchanger (25) passes through the four-way switching valve (22) and then is sucked into the compressor (21) and compressed. The indoor unit (12) supplies the air cooled in the indoor heat exchanger (25) to the room.
  • the air conditioner (10) performs heating operation.
  • the four-way selector valve (22) is set to the second state.
  • the outdoor fan (15) and the indoor fan (16) are operated.
  • Refrigeration cycle is performed in the refrigerant circuit (20). Specifically, the refrigerant discharged from the compressor (21) flows into the indoor heat exchanger (25) through the four-way switching valve (22), dissipates heat to the indoor air, and condenses. The refrigerant flowing out of the indoor heat exchanger (25) expands when passing through the expansion valve (24), then flows into the outdoor heat exchanger (23), absorbs heat from the outdoor air, and evaporates. The refrigerant that has flowed out of the outdoor heat exchanger (23) passes through the four-way switching valve (22) and then is sucked into the compressor (21) and compressed. The indoor unit (12) supplies the air heated in the indoor heat exchanger (25) to the room.
  • the outdoor heat exchanger (23) functions as an evaporator during the heating operation.
  • the evaporation temperature of the refrigerant in the outdoor heat exchanger (23) may be lower than 0 ° C.
  • the moisture in the outdoor air becomes frost and the outdoor heat exchanger (23 ). Therefore, the air conditioner (10) performs the defrosting operation every time the duration time of the heating operation reaches a predetermined value (for example, several tens of minutes).
  • the four-way switching valve (22) When starting the defrosting operation, the four-way switching valve (22) is switched from the second state to the first state, and the outdoor fan (15) and the indoor fan (16) are stopped.
  • the refrigerant circuit (20) during the defrosting operation the high-temperature refrigerant discharged from the compressor (21) is supplied to the outdoor heat exchanger (23).
  • the frost adhering to the surface In the outdoor heat exchanger (23), the frost adhering to the surface is heated and melted by the refrigerant.
  • the refrigerant that has radiated heat in the outdoor heat exchanger (23) sequentially passes through the expansion valve (24) and the indoor heat exchanger (25), and is then sucked into the compressor (21) and compressed.
  • the heating operation is resumed. That is, the four-way switching valve (22) is switched from the first state to the second state, and the operation of the outdoor fan (15) and the indoor fan (16) is resumed.
  • the heat exchanger (30) includes one first header collecting pipe (31), one second header collecting pipe (32), and a number of flat tubes (33). And a number of fins (36).
  • the first header collecting pipe (31), the second header collecting pipe (32), the flat pipe (33), and the fin (36) are all made of an aluminum alloy and are joined to each other by brazing.
  • the first header collecting pipe (31) and the second header collecting pipe (32) are both formed in a vertically long cylindrical shape, one at the left end of the heat exchanger (30) and the other at the right end of the heat exchanger (30). Respectively.
  • the flat tube (33) is a heat transfer tube having a flat cross-sectional shape, and has a flat side surface (33a) and an arc that continues to the side surface (33a) and protrudes outward. Surface (33b).
  • Each flat tube (33) is inserted into a tube insertion portion (46) of a notch (45) described later.
  • the circular arc surface (33b) of the flat tube (33) corresponds to an end portion in the insertion direction of the flat tube (33) into the notch (45).
  • the flat tubes (33) are arranged side by side in a state where the flat side surfaces (33a) face each other.
  • Each flat tube (33) has a plurality of fluid passages (34).
  • One end of each of the flat tubes (33) arranged in the vertical direction is inserted into the first header collecting pipe (31), and the other end is inserted into the second header collecting pipe (32).
  • the fins (36) are plate-like fins extending in the arrangement direction of the flat tubes (33), and are arranged at regular intervals in the extending direction of the flat tubes (33). That is, the fin (36) is disposed so as to be substantially orthogonal to the extending direction of the flat tube (33).
  • the fin (36) is a vertically long plate-like fin formed by pressing a metal plate.
  • the fin (36) has a number of elongated notches (45) extending in the width direction of the fin (36) from the front edge (38) of the fin (36).
  • a large number of notches (45) are formed at regular intervals in the longitudinal direction of the fin (36).
  • a portion closer to the lee of the notch portion (45) constitutes a tube insertion portion (46) into which the flat tube (33) is inserted.
  • the flat tube (33) is inserted into the tube insertion portion (46) and joined to the edges (46a, 46b) of the tube insertion portion (46) by brazing.
  • the edge (46a, 46b) of the tube insertion part (46) includes a linear edge (46a) corresponding to the side surface (33a) of the flat tube (33) and the linear edge (46a). And an arcuate edge (46b) corresponding to the arc surface (33b) of the flat tube (33). That is, the edge portions (46a, 46b) of the tube insertion portion (46) are portions joined to the flat tube (33), and the shape thereof corresponds to the shape of the flat tube (33).
  • the tube insertion portion (46) has a vertical width (that is, the interval between the straight edges (46a)) substantially equal to the thickness of the flat tube (33), and the length is the width of the flat tube (33). Is substantially equal.
  • the entire circumference of the edge portions (46a, 46b) of the tube insertion portion (46), that is, the straight edge portion (46a) and the arcuate edge portion (46b) go to the edge. It is bent so as to incline inward. Specifically, in one tube insertion portion (46), the opposing linear edge portion (46a) is bent into a substantially C shape. Further, the edge (46a, 46b) of the tube insertion part (46) has a bending height H of the linear edge part (46a) greater than a bending height H (not shown) of the arcuate edge part (46b). Is also formed to be large (high).
  • the fin (36) has a plurality of heat transfer portions (37) adjacent to each other up and down across the flat tube (33), and one leeward continuous to the leeward end of each heat transfer portion (37).
  • a side plate portion (47) is provided.
  • each louver (50) is formed by raising the heat-transfer part (37) and the leeward side board part (47). That is, each louver (50) is formed by making a plurality of slit-like cuts in the heat transfer part (37) and the leeward side plate part (47), and plastically deforming so as to twist the part between the adjacent cuts. ing.
  • each louver (50) is substantially parallel to the front edge (38) of the heat transfer section (37). That is, the longitudinal direction of each louver (50) is the vertical direction.
  • a plurality of louvers (50) extending in the vertical direction are formed side by side from the windward side toward the leeward side.
  • the leeward side plate portion (47) of the fin (36) is formed with a water guiding rib (71).
  • the water guiding rib (71) is a long and narrow groove extending vertically along the leeward end of the leeward plate (47), and is formed from the upper end to the lower end of the leeward plate (47). .
  • the fin (36) is formed with a tab (48) for maintaining a distance from the adjacent fin (36).
  • the tab (48) is a rectangular piece formed by cutting and raising the fin (36). The tab (48) keeps the space between the fins (36) by the protrusions coming into contact with the adjacent fins (36).
  • a substantially V-shaped groove (60) is formed.
  • the flat tube (33) and the tube insertion portion (46) are brazed, and the flat tube (33) is joined to the edges (46a, 46b) of the tube insertion portion (46).
  • the groove (60) is formed between the flat tube (33) and the edge portion (46a, 46b) of the tube insertion portion (46)
  • the molten brazing material is subjected to the above-mentioned groove ( 60).
  • the flat tube (33) is securely joined to the fin (36).
  • the groove (60) is formed over the entire periphery of the edge (46a, 46b) of the tube insertion portion (46)
  • the entire periphery of the flat tube (33) and the fin (36) are surely secured. Close contact with.
  • the molten brazing material actively flows into the groove (60) as described above, the molten brazing material is less likely to flow between the fins (36). That is, the amount of brazing material that tends to flow between the fins (36) is suppressed.
  • the groove (60) is formed over the entire circumference of the edge (46a, 46b) of the pipe insertion portion (46), it is possible to sufficiently earn the amount of brazing material flowing into the groove (60). As a result, the amount of brazing material that tends to flow between the fins (36) is further suppressed. Thereby, the state which fins (36) contact via a brazing material can be avoided.
  • the vertical width of the tube insertion portion (46) (that is, the linear edge portion). (Interval between (46a)) is narrower than the thickness of the flat tube (33). That is, before the flat tube (33) is inserted into the tube insertion portion (46), the dimension L1 shown in FIG. 6 is smaller than the dimension L2 shown in FIG. Therefore, in a state where the flat tube (33) is inserted into the tube insertion portion (46), the edge portions (46a, 46b) of the tube insertion portion (46) are securely adhered to the flat tube (33) by its elastic force. be able to. Thereby, since a flat tube (33) and a fin (36) can be joined reliably, the heat transfer amount between a flat tube (33) and a fin (36) can fully be ensured.
  • the edge (46a, 46b) to which the flat tube (33) of the notch (45) is joined that is, the edge (46a, 46b) of the tube insertion part (46).
  • the brazing material can be actively flowed into the groove (60) by capillary action. Therefore, since a sufficient amount of brazing material can be secured at the joint between the flat tube (33) and the notch (45), the flat tube (33) and the fin (36) can be reliably bonded.
  • the brazing material can be actively flowed into the groove (60), the amount of the brazing material flowing between the fins (36) can be suppressed accordingly. Thereby, the state which fins (36) will contact via a brazing material can be avoided. Therefore, increase in ventilation resistance between the fins (36) can be prevented, and as a result, it is possible to prevent the heat exchange efficiency of the heat exchanger (30) from decreasing.
  • the entire circumference of the edge (46a, 46b) is bent so that the entire circumference of the edge (46a, 46b) of the tube insertion part (46) is inclined inward as it goes to the edge.
  • the groove (60) can be formed on the surface. Therefore, the amount of brazing material flowing into the groove (60) can be increased, and thereby the amount of brazing material flowing between the fins (36) can be further suppressed.
  • the bending height H of the linear edge (46a) is greater than the bending height H of the arcuate edge (46b) at the edges (46a, 46b) of the tube insertion portion (46). It is formed to be (high). For this reason, the arc-shaped edge portion (46b) is not easily broken when the edge portions (46a, 46b) are bent. Thereby, a substantially V-shaped groove
  • the present invention is useful for a heat exchanger including a flat tube and fins and an air conditioner including the heat exchanger.
  • Air conditioner 20 Refrigerant circuit 30 heat exchanger 33 Flat tube 36 fins 45 Notch

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Un tube plat (33) est inséré dans une partie d'insertion de tube (46) d'une ailette (36), et relié à cette dernière par brasage. Les bords (46a, 46b) de la partie d'insertion de tube (46) sont pliées de manière à s'incliner vers l'intérieur lors de l'approche de la pointe du tube.
PCT/JP2012/000382 2011-01-21 2012-01-23 Échangeur de chaleur et climatiseur WO2012098915A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011011298A JP2012154498A (ja) 2011-01-21 2011-01-21 熱交換器および空気調和機
JP2011-011298 2011-01-21

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WO2012098915A1 true WO2012098915A1 (fr) 2012-07-26

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014156990A (ja) * 2013-02-18 2014-08-28 Mitsubishi Electric Corp 空気調和機の熱交換器
EP3561430A3 (fr) * 2018-04-25 2019-11-06 Panasonic Intellectual Property Management Co., Ltd. Échangeur de chaleur

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3421919A4 (fr) * 2016-02-24 2019-11-06 Mitsubishi Electric Corporation Échangeur de chaleur

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Publication number Priority date Publication date Assignee Title
JPS5238761U (fr) * 1975-09-12 1977-03-18
JPS5274552U (fr) * 1975-12-02 1977-06-03
JPS55107897A (en) * 1979-02-09 1980-08-19 Nippon Denso Co Ltd Heat exchanger
JPS58127092A (ja) * 1982-01-25 1983-07-28 Nippon Denso Co Ltd 熱交換器及びその製法
JPH02169177A (ja) * 1988-12-16 1990-06-29 Matsushita Refrig Co Ltd 熱交換器の製造方法
JPH0560482A (ja) * 1991-08-29 1993-03-09 Showa Alum Corp 熱交換器の製造方法
JPH0590173U (ja) * 1992-04-20 1993-12-07 住友軽金属工業株式会社 フィン・チューブ式熱交換器
JPH09310993A (ja) * 1996-05-22 1997-12-02 Nippon Light Metal Co Ltd 熱交換器の製造方法及び熱交換器
JP2003214791A (ja) * 2002-01-23 2003-07-30 Mitsubishi Electric Corp 熱交換器

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5238761U (fr) * 1975-09-12 1977-03-18
JPS5274552U (fr) * 1975-12-02 1977-06-03
JPS55107897A (en) * 1979-02-09 1980-08-19 Nippon Denso Co Ltd Heat exchanger
JPS58127092A (ja) * 1982-01-25 1983-07-28 Nippon Denso Co Ltd 熱交換器及びその製法
JPH02169177A (ja) * 1988-12-16 1990-06-29 Matsushita Refrig Co Ltd 熱交換器の製造方法
JPH0560482A (ja) * 1991-08-29 1993-03-09 Showa Alum Corp 熱交換器の製造方法
JPH0590173U (ja) * 1992-04-20 1993-12-07 住友軽金属工業株式会社 フィン・チューブ式熱交換器
JPH09310993A (ja) * 1996-05-22 1997-12-02 Nippon Light Metal Co Ltd 熱交換器の製造方法及び熱交換器
JP2003214791A (ja) * 2002-01-23 2003-07-30 Mitsubishi Electric Corp 熱交換器

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014156990A (ja) * 2013-02-18 2014-08-28 Mitsubishi Electric Corp 空気調和機の熱交換器
EP3561430A3 (fr) * 2018-04-25 2019-11-06 Panasonic Intellectual Property Management Co., Ltd. Échangeur de chaleur

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