WO2014045629A1 - 熱交換器 - Google Patents
熱交換器 Download PDFInfo
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- WO2014045629A1 WO2014045629A1 PCT/JP2013/062933 JP2013062933W WO2014045629A1 WO 2014045629 A1 WO2014045629 A1 WO 2014045629A1 JP 2013062933 W JP2013062933 W JP 2013062933W WO 2014045629 A1 WO2014045629 A1 WO 2014045629A1
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- WIPO (PCT)
- Prior art keywords
- tank
- width direction
- communication channel
- length
- heat exchanger
- Prior art date
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Classifications
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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
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
- F28F1/045—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular with assemblies of stacked elements
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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
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
- F28F9/0221—Header boxes or end plates formed by stacked elements
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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
- 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
- F28D1/03—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 plate-like or laminated conduits
- F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other
- F28D1/0325—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
- F28D1/0333—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
- F28D1/0341—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members with U-flow or serpentine-flow inside the 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
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
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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
Definitions
- the present invention relates to a multiflow type heat exchanger.
- a laminated heat exchanger in which a large number of core bodies (flat tubes) are laminated is known as a multiflow type heat exchanger (for example, see Patent Document 1).
- a multiflow type heat exchanger for example, see Patent Document 1.
- two tanks are provided on the upper windward side and the leeward side, and two tanks are provided on the lower windward side and the leeward side.
- both ends of the core body in the stacking direction are closed by end plates.
- the end plate at one end is formed with a flow path for communicating the windward and leeward tanks located on the upper side.
- the refrigerant circulating in the tank flows from one tank on the upper side to the other tank on the upper side through a flow path formed in the end plate.
- the pressure of the circulating refrigerant is applied to the plate surface of the end plate in a direction orthogonal to the plate surface.
- the end plate may be deformed. Therefore, it is preferable to increase the rigidity of the end plate.
- the thickness of the end plate increases the weight of the heat exchanger and may increase the cost by increasing the thickness of the end plate.
- the reinforcing ribs are provided on the end plate, a complicated structure is formed. Therefore, a portion where stress is easily concentrated is formed, and it becomes difficult to suppress the deformation of the end plate, and the complicated structure is obtained. The cost may increase.
- an object of the present invention is to provide a heat exchanger that can suppress pressure deformation with a simple configuration.
- the heat exchanger of the present invention communicates with a plurality of flat tubes to be stacked, a plurality of fins provided between adjacent flat tubes, and a first refrigerant flow path formed inside the flat tubes, and the flat tubes
- a first tank provided on one side of the longitudinal direction of the plurality of flat tubes and communicated with a second refrigerant flow path formed inside the flat tubes, and in a longitudinal direction of the flat tubes.
- a wall is provided that is provided on one side, is provided across the stacking direction, and is provided adjacent to the first tank, and a wall that forms a communication channel that connects the first tank and the second tank.
- a communication member, and a direction perpendicular to the stacking direction and adjacent to the first tank and the second tank is defined as a width direction, and a direction perpendicular to the width direction and the stacking direction is defined as a height direction.
- Communication The road has a throttle portion whose outer shape of the wall body is formed in a shape longer in the width direction than in the height direction, and is formed at the center in the width direction, and the throttle portion is an outer wall surface of the wall body.
- the length of the outer dimension in the height direction of the communication flow path is H
- the communication flow path When the length having the maximum outer dimension in the width direction is W, the radius of curvature R of the throttle portion is R ⁇ 0.2H, and the outer dimension is the minimum in the height direction of the throttle portion of the communication channel.
- the length L is L ⁇ 0.9H, and the portion of the length H where the outer dimension is maximum in the height direction is outside the width direction by 1/4 W or more from the portion of the communication channel length L. It is provided in a position.
- the pressure deformation of the communication member can be suppressed by providing the communication channel with a predetermined shape while providing the throttle portion in the communication channel.
- the throttle part is simply provided, stress concentrates on the throttle part, and the communication member may be pressure-deformed.
- the radius of curvature R of the throttle portion of the communication channel is set to R ⁇ 0.2H, the gradient of the throttle portion can be moderated and the stress concentration can be suppressed.
- the length L of the throttle portion to L ⁇ 0.9H, the pressure receiving area can be reduced and the rigidity can be increased.
- the portion with the length H having the maximum outside dimension in the height direction at a position that is 1/4 W or more in the width direction outside of the portion with the length L of the throttle portion in the width direction.
- the opening of the first tank that communicates with the road does not overlap the opening of the second tank that communicates with the communication channel. For this reason, since the pressure receiving surface from the 1st tank which a communicating flow path receives, and the pressure receiving surface from the 2nd tank which a communicating flow path receives do not overlap, the pressure rise by duplication of a pressure receiving surface can be suppressed. .
- a virtual oval having a shape in which a line passing through a portion having a length H where the outer dimension is maximum in the height direction is an axis, and a portion on the outer side in the width direction from the axis is developed symmetrically about the axis.
- the outer shape is preferably formed in a shape shorter in the width direction than in the height direction.
- the outer shape of the virtual oval can be formed shorter in the width direction than in the height direction. For this reason, the communication channel can be shortened in the width direction, and the configuration of the heat exchanger itself can be made compact.
- the communication channel is preferably 0.5 ⁇ H / W ⁇ 1.0.
- the communication channel can be made longer in the width direction than in the height direction, the first tank and the second tank adjacent to each other in the width direction do not overlap with each other.
- the second tank can be suitably connected to the communication channel.
- FIG. 1 is a schematic configuration diagram of a heat exchanger according to the present embodiment.
- FIG. 2 is a perspective view around the end plate of the heat exchanger.
- FIG. 3 is a cross-sectional perspective view around the end plate of the heat exchanger cut along a plane orthogonal to the width direction.
- FIG. 4 is a partial cross-sectional view around the end plate of the heat exchanger cut along a plane orthogonal to the width direction.
- FIG. 5 is a cross-sectional view of the communication channel cut along a plane orthogonal to the stacking direction.
- FIG. 1 is a schematic configuration diagram of a heat exchanger according to the present embodiment.
- FIG. 2 is a perspective view around the end plate of the heat exchanger.
- FIG. 3 is a cross-sectional perspective view around the end plate of the heat exchanger cut along a plane orthogonal to the width direction.
- FIG. 4 is a partial cross-sectional view around the end plate of the heat exchanger cut along a plane orthogonal to the width direction.
- FIG. 5 is a cross-sectional view of the communication channel cut along a plane orthogonal to the stacking direction. 2 to 4 are diagrams in which the vertical direction (longitudinal direction) in FIG. 1 is reversed.
- the heat exchanger 1 of the present embodiment is a multi-flow stacked heat exchanger, and is used as an evaporator (evaporator) of an air conditioner mounted on an automobile, for example.
- the heat exchanger 1 of a present Example may be applied to any as long as it is a multiflow type laminated heat exchanger, and is not particularly limited.
- the heat exchanger 1 of this embodiment includes a plurality of flat tubes 2, a plurality of corrugated fins 3 (see FIG. 4), and a pair of end plates 4.
- the plurality of flat tubes 2 are stacked in the stacking direction, the plurality of corrugated fins 3 are provided between the flat tubes 2 adjacent to each other in the stacking direction, and the pair of end plates 4 are disposed on both sides in the stacking direction. Is provided.
- the plurality of stacked flat tubes 2, the plurality of corrugated fins 3, and the pair of end plates 4 are integrally joined by brazing.
- the flat tube 2 is formed to extend in the longitudinal direction by joining a pair of press-molded molding plates.
- the flat tube 2 has a flat shape in a cross section cut by a surface orthogonal to the longitudinal direction, and is laminated in a direction orthogonal to the flat surface.
- the flat tube 2 has a first upper opening 11a and a second upper opening 12a penetratingly formed in one end part (upper end part) in the longitudinal direction in the stacking direction, and the other end part (lower part in the longitudinal direction)
- the first lower opening 21a and the second lower opening 22a are formed penetratingly in the stacking direction at the end portion on the side.
- the first upper opening 11a and the second upper opening 12a are arranged side by side in the width direction orthogonal to the longitudinal direction and the stacking direction. Similarly, the first lower opening 21a and the second lower opening 22a are also arranged in the width direction. Is provided.
- first upper opening 11a and the second upper opening 12a a plurality of flat tubes 2 are stacked in the stacking direction, so that the plurality of first upper openings 11a and the second upper opening 12a are connected in the stacking direction.
- the plurality of first upper openings 11 a connected in the stacking direction function as the first upper tank 11.
- the plurality of second upper openings 12 a connected in the stacking direction function as the second upper tank 12.
- the first upper opening 11 a and the second upper opening 12 a are part of the first upper tank 11 and the second upper tank 12. Therefore, the first upper tank 11 and the second upper tank 12 extend in the stacking direction adjacent to one end in the longitudinal direction of the plurality of flat tubes 2 to be stacked in parallel to the width direction.
- the air A flowing in the heat exchanger 1 flows from the upstream side in the width direction toward the downstream side, and the first upper tank 11 is provided on the downstream side in the width direction, and the second upper tank 12 Is provided on the upstream side in the width direction.
- the first lower opening 21a and the second lower opening 22a are formed by stacking a plurality of flat tubes 2 in the stacking direction in the same manner as the first upper opening 11a and the second upper opening 12a.
- the first lower opening 21a and the second lower opening 22a are connected in the stacking direction.
- the plurality of first lower openings 21 a connected in the stacking direction function as the first lower tank 21.
- the plurality of second lower openings 22 a connected in the stacking direction function as the second lower tank 22.
- the first lower opening 21 a and the second lower opening 22 a are part of the first lower tank 21 and the second lower tank 22.
- the first lower tank 21 and the second lower tank 22 extend in the stacking direction, adjacent to the other end in the longitudinal direction of the plurality of flat tubes 2 to be stacked in parallel to the width direction. Are formed respectively.
- the first lower tank 21 is provided on the downstream side in the width direction
- the second lower tank 22 is provided on the upstream side in the width direction.
- the flat tube 2 has a first refrigerant channel and a second refrigerant channel formed therein.
- the first refrigerant flow path is a flow path that connects the first upper tank 11 (first upper opening 11a) and the first lower tank 21 (first lower opening 21a).
- the second refrigerant channel is a channel that communicates the second upper tank 12 (second upper opening 12a) and the second lower tank 22 (second lower opening 22a).
- the corrugated fin 3 is a corrugated plate having a transverse wave shape extending in the longitudinal direction, and has a mountain portion and a valley portion extending in the width direction. For this reason, the air A flowing in the width direction of the heat exchanger 1 is cooled by passing through the corrugated fins 3.
- the pair of end plates 4 close or adjoin end portions in the stacking direction of the first upper tank 11, the second upper tank 12, the first lower tank 21, and the second lower tank 22.
- the first upper tank 11 and the second upper tank 12 communicate with each other, and the adjacent first lower tank 21 and second lower tank 22 communicate with each other.
- the end plate 4 is formed so as to extend in the longitudinal direction by joining a pair of press-molded forming plates in the same manner as the flat tube 2.
- one end plate 4 includes a refrigerant inlet Rin through which refrigerant flows into the heat exchanger 1 at one end (upper end) in the longitudinal direction, and the heat exchanger 1.
- a refrigerant outlet Rout from which the refrigerant flows out.
- the refrigerant inlet Rin is connected to the first upper tank 11, and the refrigerant outlet Rout is connected to the second upper tank 12.
- the other end plate 4 has the other end in the longitudinal direction (the end on the lower side) at the end of the first lower tank 21 and the end of the second lower tank 22.
- a communication channel 31 that communicates with the portion is formed.
- a partition 18 is installed in the middle of the first lower tank 21 in the stacking direction.
- a partition portion 19 is installed in the middle portion of the second upper tank 12 in the stacking direction.
- the refrigerant when a refrigerant flows from the outside into the heat exchanger 1 configured as described above, the refrigerant is one end in the stacking direction of the first upper tank 11 via the refrigerant inlet Rin. Flow into.
- the refrigerant flowing into one end of the first upper tank 11 passes through the first refrigerant flow path in the flat tube 2 on one end side (right side in FIG. 1) of the heat exchanger 1 with the partition portion 18 in between.
- the refrigerant that has flowed into the first upper tank 11 on the other side flows through the first refrigerant flow path in the flat tube 2 and flows into the first lower tank 21.
- the refrigerant flowing into the first lower tank 21 flows toward the other end (left side in FIG. 1) in the stacking direction of the first lower tank 21.
- the refrigerant that has flowed to the other end of the first lower tank 21 flows into the other end in the stacking direction of the second lower tank 22 via the communication channel 31.
- the refrigerant that has flowed into the other end of the second lower tank 22 flows through the second refrigerant flow path in the flat tube 2 on the other end side of the heat exchanger 1 with the partition portion 19 in between, and the second upper tank It flows into the tank 12. Since the second upper tank 12 is partitioned by the partitioning portion 19, the refrigerant that has flowed through the second upper tank 12 flows again through the second refrigerant flow path in the flat tube 2 and enters the second lower tank 22. Inflow. Then, the refrigerant flowing into the second lower tank 22 flows into the second lower tank 22 on one end side (right side in FIG. 1) of the heat exchanger 1 with the partition portion 19 interposed therebetween.
- the refrigerant that has flowed into the second lower tank 22 on one side flows through the second refrigerant flow path in the flat tube 2 and flows into the second upper tank 12.
- the refrigerant flowing into the second upper tank 12 flows toward one end side (right side in FIG. 1) in the stacking direction of the second upper tank 12.
- the refrigerant that has flowed to one end of the second upper tank 12 flows out of the heat exchanger 1 through the refrigerant outlet Rout.
- the heat exchanger 1 is configured as described above.
- the present invention is not limited to the above configuration, and the position and number of partitions 18 and 19, the position and number of communication channels 31, the refrigerant inlet The positions of Rin and the refrigerant outlet Rout may be appropriately changed so that the flow path through which the refrigerant flows becomes a predetermined flow path.
- the communication channel 31 provided in the end plate 4 (communication member) of the present embodiment is a channel that connects the first lower tank 21 and the second lower tank 22. 2 to 4, the communication flow path 31 is illustrated so as to be located on the upper right side.
- the first lower tank 21 and the second lower tank 22 are described as being applied to the communication flow path 31 that communicates with each other.
- the present invention is not particularly limited as long as it is a flow path that communicates adjacent tanks.
- the communication channel 31 is formed by a wall body 32 provided on the end plate 4. As shown in FIG. 5, the outer shape of the wall body 32 of the communication channel 31 is such that the shape seen from the stacking direction is in the width direction compared to the height direction (longitudinal direction) orthogonal to the stacking direction and the width direction. It has a long shape.
- the outer shape of the wall body 32 of the communication flow path 31 is symmetrical in the vertical direction (symmetric in the height direction) and laterally symmetrical (symmetric in the width direction) when viewed from the stacking direction.
- the communication channel 31 is formed with a throttle portion 34 at the center in the width direction.
- the outer wall surface of the wall body 32 is a curved surface having a predetermined radius of curvature R formed in a convex shape inside the communication channel 31.
- the communication flow path 31 becomes a narrow flow path at the center in the width direction, and becomes a wide flow path on both sides in the width direction.
- the thickness of the wall 32 of the communication channel 31 is, for example, 0.5 mm to 1.0 mm.
- the communication channel 31 viewed from the stacking direction has a length H that maximizes the outer dimension (dimension on the outer wall surface of the wall body 32) in the height direction. That is, the length H is a length obtained by connecting the pair of top portions 32a having the maximum outer dimension in the height direction.
- the pair of top portions 32a in the length H are provided on both sides in the width direction.
- the communication channel 31 viewed from the stacking direction has a length L that minimizes the outer dimension in the height direction. That is, the length L is a length obtained by connecting a pair of valley portions 32b formed in the narrowed portion 34 having the smallest outer dimension in the height direction. At this time, the length L is a length passing through the center in the width direction.
- the length of the communication channel 31 seen from the stacking direction is W, which is the maximum outside dimension in the width direction. That is, the length W is a length obtained by connecting a pair of top portions 32c having the maximum outer dimension in the width direction. Specifically, the length W is W ⁇ 40 mm.
- the communication channel 31 has a shape that is longer in the width direction than in the height direction (longitudinal direction), 0.5 ⁇ H / W ⁇ 1.0. For this reason, the first lower tank 21 and the second lower tank 22 adjacent in the width direction can be suitably connected to the communication flow path 31.
- the communication channel 31 configured as described above is provided with a throttle unit 34 in the center in the width direction in order to suppress pressure deformation of the communication channel 31, but the throttle unit 34 is simply provided with the throttle unit 34. Since there is a possibility that stress concentrates on 34, the shape of the communication channel 31 is set to the shape described below.
- the communication channel 31 has a radius of curvature R on the outer wall surface of the wall body 32 of the throttle portion 34 such that R ⁇ 0.2H.
- the narrowed portion 34 is formed such that the radius of curvature R satisfies R ⁇ 0.2H, so that the gradient of the narrowed portion 34 becomes gentle and the concentration of stress can be suppressed.
- the communication channel 31 has a length L in the height direction of the throttle portion 34, L ⁇ 0.9H. That is, the throttle portion 34 is formed such that the length L is L ⁇ 0.9H, thereby reducing the pressure receiving area in the plane orthogonal to the stacking direction of the communication flow path 31 and the wall of the throttle portion 34. 32 can increase the rigidity.
- the top portion 32 a having a length H is located on the outer side in the width direction from the valley portion 32 b having a length L by 1 ⁇ 4 W.
- a line passing through the apex 32a having a length H is defined as an axis I
- a shape in which a portion outside the axis I in the width direction is developed symmetrically about the axis I is defined as a virtual oval O.
- the outer diameter of the virtual oval O is a shape that does not overlap. That is, the length C in the width direction of the virtual oval O is C ⁇ W / 2.
- the pressure receiving surface from the first lower tank 21 received by the communication channel 31 from the stacking direction and the pressure receiving surface from the second lower tank 22 received by the communication channel 31 do not overlap. It is possible to suppress an increase in pressure due to.
- the outer shape of the virtual oval O is shorter in the width direction than in the height direction.
- the pressure flow of the end plate 4 is suppressed by providing the communication channel 31 with the above-mentioned shape while providing the throttle portion 34 in the communication channel 31. be able to.
- the outer shape of the virtual oval O can be formed in a shape shorter in the width direction than in the height direction. For this reason, the communication flow path 31 can be made short in the width direction, and the configuration of the heat exchanger 1 itself can be made compact.
- the communication flow path 31 can be made longer in the width direction than in the height direction, so the first lower tank 21 and the second lower tank 22 that are adjacent in the width direction. Can be suitably connected to the communication channel 31.
- first lower tank 21 and the second lower tank 22 are applied to the communication flow path 31 communicating with each other, but the first upper tank 11 and the second upper tank 12 are applied to the communication flow path. May be.
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- Physics & Mathematics (AREA)
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- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
2 偏平チューブ
3 コルゲートフィン
4 エンドプレート
11 第1上部タンク
11a 第1上部開口
12 第2上部タンク
12a 第2上部開口
21 第1下部タンク
21a 第1下部開口
22 第2下部タンク
22a 第2下部開口
31 連通流路
32 壁体
32a 高さ方向の頂部
32b 高さ方向の谷部
32c 幅方向の頂部
34 絞り部
Rin 冷媒入口
Rout 冷媒出口
I 軸線
O 仮想オーバル
Claims (3)
- 積層される複数の偏平チューブと、
隣接する前記偏平チューブの間に設けられる複数のフィンと、
前記偏平チューブの内部に形成される第1冷媒流路に連通し、前記偏平チューブの長手方向の一方側に設けられ、前記複数の偏平チューブの積層方向に亘って設けられる第1タンクと、
前記偏平チューブの内部に形成される第2冷媒流路に連通し、前記偏平チューブの長手方向の一方側に設けられ、前記積層方向に亘って設けられると共に前記第1タンクに隣接して設けられる第2タンクと、
前記第1タンクと前記第2タンクとを連通する連通流路を形成する壁体が設けられる連通部材と、を備え、
前記積層方向に直交すると共に前記第1タンクと前記第2タンクとが隣接する方向を幅方向とし、前記幅方向及び前記積層方向に直交する方向を高さ方向とすると、
前記積層方向から見た前記連通流路は、その前記壁体の外形が前記高さ方向に比して前記幅方向に長い形状に形成され、且つ、前記幅方向の中央に形成される絞り部を有し、
前記絞り部は、前記壁体の外壁面が、前記連通流路の内側に凸となる所定の曲率半径Rで形成される曲面となっており、
前記連通流路の前記高さ方向において外側寸法が最大となる長さをHとし、前記連通流路の前記幅方向において外側寸法が最大となる長さをWとすると、
前記絞り部の前記曲率半径Rは、R≧0.2Hであり、
前記連通流路の前記絞り部の前記高さ方向において外側寸法が最小となる長さLは、L≦0.9Hであり、
前記高さ方向において外側寸法が最大となる前記長さHの部位は、前記連通流路の長さLとなる部位から1/4W以上の幅方向外側となる位置に設けられることを特徴とする熱交換器。 - 前記高さ方向において外側寸法が最大となる前記長さHの部位を通る線を軸線とし、
前記軸線から幅方向外側の部位を、前記軸線を中心にして線対称に展開した形状である仮想オーバルの外形は、前記高さ方向に比して前記幅方向に短い形状に形成されていることを特徴とする請求項1に記載の熱交換器。 - 前記連通流路は、0.5<W/H<1.0であることを特徴とする請求項1または2に記載の熱交換器。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201380040318.6A CN104508419A (zh) | 2012-09-19 | 2013-05-08 | 换热器 |
DE112013004567.2T DE112013004567T5 (de) | 2012-09-19 | 2013-05-08 | Wärmetauscher |
US14/417,901 US20150176921A1 (en) | 2012-09-19 | 2013-05-08 | Heat exchanger |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012205683A JP2014059123A (ja) | 2012-09-19 | 2012-09-19 | 熱交換器 |
JP2012-205683 | 2012-09-19 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2014045629A1 true WO2014045629A1 (ja) | 2014-03-27 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2013/062933 WO2014045629A1 (ja) | 2012-09-19 | 2013-05-08 | 熱交換器 |
Country Status (5)
Country | Link |
---|---|
US (1) | US20150176921A1 (ja) |
JP (1) | JP2014059123A (ja) |
CN (1) | CN104508419A (ja) |
DE (1) | DE112013004567T5 (ja) |
WO (1) | WO2014045629A1 (ja) |
Families Citing this family (2)
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JP6616115B2 (ja) * | 2015-07-30 | 2019-12-04 | 株式会社マーレ フィルターシステムズ | 熱交換器 |
CN105423803A (zh) * | 2016-01-12 | 2016-03-23 | 扬州英谛车材实业有限公司 | 扁管加凸包不扩口炉焊式水箱 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0674686A (ja) * | 1992-08-31 | 1994-03-18 | Mitsubishi Heavy Ind Ltd | 積層型熱交換器 |
JPH08121988A (ja) * | 1994-10-27 | 1996-05-17 | Zexel Corp | 積層型熱交換器 |
JP2005090948A (ja) * | 2003-08-08 | 2005-04-07 | Showa Denko Kk | 熱交換器およびエバポレータ |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AU663964B2 (en) * | 1992-08-31 | 1995-10-26 | Mitsubishi Jukogyo Kabushiki Kaisha | Stacked heat exchanger |
CN1333229C (zh) * | 2000-12-28 | 2007-08-22 | 昭和电工株式会社 | 层状热交换器 |
JP2006010102A (ja) * | 2004-06-22 | 2006-01-12 | Sanden Corp | 積層型熱交換器およびその製造方法 |
JP2006029697A (ja) * | 2004-07-16 | 2006-02-02 | Denso Corp | 冷媒蒸発器 |
JP2006183962A (ja) * | 2004-12-28 | 2006-07-13 | Denso Corp | 蒸発器 |
JP2007093025A (ja) * | 2005-09-27 | 2007-04-12 | Showa Denko Kk | 熱交換器およびその製造方法 |
-
2012
- 2012-09-19 JP JP2012205683A patent/JP2014059123A/ja active Pending
-
2013
- 2013-05-08 CN CN201380040318.6A patent/CN104508419A/zh active Pending
- 2013-05-08 DE DE112013004567.2T patent/DE112013004567T5/de not_active Ceased
- 2013-05-08 WO PCT/JP2013/062933 patent/WO2014045629A1/ja active Application Filing
- 2013-05-08 US US14/417,901 patent/US20150176921A1/en not_active Abandoned
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0674686A (ja) * | 1992-08-31 | 1994-03-18 | Mitsubishi Heavy Ind Ltd | 積層型熱交換器 |
JPH08121988A (ja) * | 1994-10-27 | 1996-05-17 | Zexel Corp | 積層型熱交換器 |
JP2005090948A (ja) * | 2003-08-08 | 2005-04-07 | Showa Denko Kk | 熱交換器およびエバポレータ |
Also Published As
Publication number | Publication date |
---|---|
DE112013004567T5 (de) | 2015-06-03 |
JP2014059123A (ja) | 2014-04-03 |
CN104508419A (zh) | 2015-04-08 |
US20150176921A1 (en) | 2015-06-25 |
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