JP2018074121A - Laminated heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a laminated heat exchanger 1 capable of preventing coolant from flowing from fin channels 310a to 310h and 320a to 320h to an end gap 302.SOLUTION: A laminated heat exchanger 1 includes: a partition wall 341 that partitions between an end gap 302 and fin channels 310a to 310h, 320a to 320h to prevent coolant from flowing from the fin channels 310a to 310h, 320a to 320h to the end gap 302; and a closed part 40 which closes the end gap 302 to prevent the coolant from flowing into the end gap 302. With this, flow of the coolant in the end gap 302 is sufficiently shut-off.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a stacked heat exchanger.

  Conventionally, in order to dissipate heat from a heating element such as a semiconductor module incorporating a semiconductor element, a multilayer heat exchanger is known in which a plurality of heat exchange tubes are arranged to sandwich the heating element from both sides. (For example, refer to Patent Document 1).

  Such a heat exchanger has a configuration in which heating elements and heat exchange tubes are alternately stacked, and the plurality of stacked heat exchange tubes are communicated with each other by a communication member, and a refrigerant is connected to each heat exchange tube. It is configured to be distributed.

  In this type of heat exchanger, in order to improve the heat exchange performance, inner fins configured as a plurality of fin passages that partition the refrigerant passage in the heat exchange tube and are arranged in the width direction are installed in the heat exchange tube. The heat transfer area is expanded to increase the heat transfer coefficient.

  Note that Patent Document 2 proposes an offset fin suitable as an inner fin.

JP 2006-5014 A JP 2013-234627 A

  In the stacked heat exchanger of Patent Document 1, an end clearance channel is formed between the inner wall of the outer shell plate constituting the heat exchange tube and one side in the width direction of the inner fin. For this reason, when the refrigerant flows from the fin channel into the end gap channel, the amount of the refrigerant flowing into the fin channel through which the original refrigerant should flow is reduced, and thus there is a problem that the expected heat dissipation performance cannot be obtained.

  On the other hand, it is conceivable to suppress the refrigerant from flowing into the end gap channel by closing the inlet of the end gap channel. However, when offset type inner fins (hereinafter referred to as offset fins) are used, the refrigerant may flow out from the plurality of fin flow paths constituted by the offset fins to the end gap flow paths.

  In view of the above points, an object of the present invention is to suppress a refrigerant from flowing from a fin channel to an end gap in a stacked heat exchanger that houses offset fins in a heat exchange tube.

In order to achieve the above object, according to the first aspect of the present invention, a plurality of heat exchange tubes (3) constituting the refrigerant flow path (30) for circulating the refrigerant to exchange heat with the heat exchange target (2). ), And a heat exchanger tube and a heat exchange target are alternately stacked in a stacking direction, and a plurality of heat exchange tubes and a heat exchange target are stacked,
An inner fin (34) housed in each of the plurality of heat exchange tubes;
Inner fin
A plurality of upstream fin portions (31a to 31h) that are arranged in the width direction and that respectively constitute upstream fin channels (310a to 310h) for circulating the refrigerant in the refrigerant channel;
It is arranged in the width direction on the downstream side in the refrigerant flow direction with respect to the plurality of upstream fin portions, and is provided offset in the width direction with respect to the corresponding upstream fin portion among the plurality of upstream fin portions. Furthermore, it is an offset fin comprising a plurality of downstream fin portions (32a to 32h) that respectively constitute downstream fin channels (320a to 320h) for circulating the refrigerant in the refrigerant channel,
The laminated heat exchanger is
Inner walls (312 and 322) which are arranged on one side in the width direction with respect to each upstream fin channel and each downstream fin channel in the heat exchange tube and constitute a refrigerant channel in the heat exchange tube A first partition wall (341) forming a first end gap (302) between the first partition wall (341) and
A first closing portion (40) that closes the first end portion gap and prevents the refrigerant from flowing into the first end portion gap.

  As described above, according to the first aspect of the present invention, it is possible to suppress the refrigerant from flowing from the fin channel to the first end gap.

The invention according to claim 5 includes a plurality of heat exchange tubes (3) constituting a refrigerant flow path (30) for circulating a refrigerant to exchange heat with the heat exchange target (2), and the heat exchange tube. A plurality of heat exchange tubes and a heat exchange target are stacked so that the heat exchange target and the heat exchange target are alternately arranged in the stacking direction,
An inner fin (34) housed in each of the plurality of heat exchange tubes;
Inner fin
A plurality of upstream fin portions (31a to 31h) that are arranged in the width direction and that respectively constitute upstream fin channels (310a to 310h) for circulating the refrigerant in the refrigerant channel;
It is arranged in the width direction on the downstream side in the refrigerant flow direction with respect to the plurality of upstream fin portions, and is provided offset in the width direction with respect to the corresponding upstream fin portion among the plurality of upstream fin portions. And a plurality of downstream fin portions (32a to 32h) that respectively constitute downstream fin passages (320a to 320h) for circulating the refrigerant in the refrigerant passage, and a plurality of upstream fin portions and a plurality of downstream portions. The side fin portions are offset fins that are alternately arranged one by one in the refrigerant flow direction, thereby circulating the refrigerant in a wavy shape that meanders in the width direction,
Of the plurality of upstream fin portions, the upstream fin portion (31a) disposed on one side in the width direction includes inner walls (312 and 322) constituting the refrigerant flow path and the upstream fin flow path of the heat exchange tube. A first upstream side wall (311a) that partitions
The downstream fin portion (32a) disposed on one side in the width direction among the plurality of downstream fin portions has a first downstream side wall (321a) that partitions the inner wall of the heat exchange tube and the downstream fin flow path. Prepared,
The refrigerant flow direction upstream end portion (400) of the first downstream side wall is disposed so as to be offset to one side in the width direction with respect to the refrigerant flow direction downstream end portion (401) of the first upstream fin portion. And
The downstream end portion (403) in the refrigerant flow direction in the first downstream side wall is connected to the upstream end portion (402) in the refrigerant flow direction in the first upstream fin portion,
The laminated heat exchanger is
The first end portion is closed by closing the first end gap (302) formed between the first upstream side wall and the first downstream side wall and the inner walls (312 and 322) constituting the refrigerant flow path in the heat exchange tube. The 1st obstruction | occlusion part (40) which suppresses a refrigerant | coolant flowing into a clearance gap is provided.

  As described above, according to the invention described in claim 5, it is possible to suppress the refrigerant from flowing from the fin channel to the first end gap.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a front view of the lamination type heat exchanger in a 1st embodiment of the present invention. It is II-II sectional drawing in FIG. FIG. 3 is a sectional view taken along line III-III in FIG. 2. It is a figure equivalent to IV-IV sectional drawing in FIG. It is a perspective view which shows the offset fin single-piece | unit in FIG. It is an enlarged view of A part in FIG. It is the elements on larger scale of the heat exchange tube in contrast, and is a figure corresponding to Drawing 6A. It is the elements on larger scale of the heat exchange tube of the laminated heat exchanger in 2nd Embodiment of this invention, and is a figure corresponding to FIG. 6A. It is the elements on larger scale of the heat exchange tube in contrast, and is a figure corresponding to Drawing 5A. It is the elements on larger scale of the heat exchange tube of the laminated heat exchanger in 3rd Embodiment of this invention, and is a figure corresponding to FIG. 5A. It is the elements on larger scale of the heat exchange tube of the laminated heat exchanger in 3rd Embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, parts that are the same or equivalent to each other are given the same reference numerals in the drawings in order to simplify the description.

(First embodiment)
A stacked heat exchanger 1 shown in FIG. 1 is a cooler that cools a heat exchange target by causing heat exchange between the refrigerant circulating in the stacked heat exchanger 1 and the heat exchange target. Specifically, the heat exchange object, that is, the cooling object is a plurality of electronic components 2 formed in a plate shape, and the stacked heat exchanger 1 cools the electronic component 2 from both sides. As the refrigerant of the stacked heat exchanger 1, for example, water (that is, cooling water) mixed with an ethylene glycol antifreeze is used.

  1 indicates the stacking direction DRst of the heat exchange tubes 3. An arrow DRtb in FIG. 1 indicates the longitudinal direction DRtb of the heat exchange tube 3. An arrow DRw in FIG. 2 indicates the width direction DRw of the heat exchange tube 3.

  In the present embodiment, the tube stacking direction DRst, the tube longitudinal direction DRtb, and the tube width direction DRw are directions intersecting each other, more precisely, directions orthogonal to each other. Further, in FIG. 1, dot hatching is added to the electronic component 2 for easy display.

  As shown in FIGS. 1 and 3, the stacked heat exchanger 1 includes a plurality of heat exchange tubes 3 formed in a flat shape in an electronic component 2 in a gap formed between adjacent heat exchange tubes 3. Are arranged in a stacked state in a state in which are arranged. That is, the heat exchange tube 3 is a heat exchange tube that is alternately laminated with the electronic component 2 in the tube lamination direction DRst. A refrigerant that exchanges heat with the electronic component 2 flows inside the heat exchange tube 3.

  The electronic component 2 is formed in a flat rectangular parallelepiped shape so as to be sandwiched by the heat exchange tube 3 adjacent to the electronic component 2 from both sides in the tube stacking direction DRst. In the present embodiment, as the electronic component 2, a semiconductor module used in an inverter circuit for a vehicle-mounted traveling motor is employed. The inverter circuit is an electric circuit that converts DC power into three-phase AC power or converts three-phase AC power into DC power. The semiconductor module is a component composed of a semiconductor element such as an IGBT and a diode, for example.

  As shown in FIG. 3, the heat exchange tube 3 has a shape in which a pair of peripheral portions in the tube width direction DRw extend in parallel along the tube longitudinal direction DRtb.

  The heat exchange tube 3 of the present embodiment is formed by laminating metal plates having high thermal conductivity such as aluminum and copper in the same manner as the heat exchange tube included in the stacked cooler disclosed in Patent Document 1. It is constructed by joining.

  Specifically, as shown in FIG. 3, the heat exchange tube 3 includes a pair of outer shell plates 31, 32, an intermediate plate 33 disposed between the pair of outer shell plates 31, 32, and an outer shell plate. 31 and 32 and a wave-shaped inner fin 50 arranged between the intermediate plate 33.

  Between the outer shell plate 31 and the intermediate plate 33, a coolant channel 30 through which the coolant flows is formed. Between the outer shell plate 32 and the intermediate plate 33, a coolant channel 30 through which the coolant flows is formed.

  In the heat exchange tube 3 of the present embodiment, since the refrigerant flows along the tube longitudinal direction DRtb, the flow direction of the refrigerant is parallel to the tube longitudinal direction DRtb.

  The pair of outer shell plates 31 and 32 are plate members that constitute the outer shell of the heat exchange tube 3. The pair of outer shell plates 31, 32, the intermediate plate 33, and the inner fin 50 are joined to each other by brazing.

  Here, a contact surface 311 that contacts the electronic component 2 is formed on one side (upper side in FIG. 1) of the outer shell plate 31 in the tube stacking direction DRst. A contact surface 321 that contacts the electronic component 2 is formed on the other side of the outer shell plate 32 in the tube stacking direction DRst (upper side in FIG. 1). The contact surfaces 311 and 321 are formed so as to face each other.

  Here, the contact surfaces 311 and 321 occupy most of the flat surface of the heat exchange tube 3. The contact surfaces 311 and 321 overlap the inner fin 50 when viewed from the tube stacking direction DRst.

  The intermediate plate 33 is a flat plate member whose outer shape viewed from the tube stacking direction DRst is substantially the same as the outer shell plates 31 and 32. The intermediate plate 33 is sandwiched between the outer shell plates 31 and 32 at the peripheral edge portion and joined to the outer shell plates 31 and 32.

  At the same time, the intermediate plate 33 is joined to the pair of outer shell plates 31 and 32 through the inner fins 50. In the intermediate plate 33, circular opening holes 33a and 33b are formed corresponding to openings of the projecting pipe portion 35 described later.

  The opening hole 33 a is a refrigerant introduction port that is arranged on one side of the intermediate plate 33 in the longitudinal direction DRtb and allows the refrigerant flowing from the refrigerant introduction pipe 4 through the supply header portion 11 to flow into the refrigerant flow path 30. The opening hole 33 b is a refrigerant outlet that is arranged on the other side in the longitudinal direction DRtb of the intermediate plate 33 and causes the refrigerant from the refrigerant flow path 30 to flow out to the discharge header portion 12.

  Since this intermediate plate 33 is provided, in the heat exchange tube 3, a two-stage refrigerant flow path 30 is formed with the intermediate plate 33 sandwiched in the tube stacking direction DRst. That is, one refrigerant flow path 30 of the two-stage refrigerant flow paths 30 is formed by one outer shell plate 31 and the intermediate plate 33 of the pair of outer shell plates 31 and 32. The other refrigerant channel 30 is formed by the other outer shell plate 32 and the intermediate plate 33 of the pair of outer shell plates 31 and 32.

  The inner fin 50 is a member that promotes heat exchange between the refrigerant flowing through the refrigerant flow path 30 and the electronic component 2. In order to promote the heat exchange, two inner fins 50 are provided as shown in FIG.

  One of the two inner fins 50 is disposed in the one refrigerant flow path 30 and the other inner fin 50 is disposed in the other refrigerant flow path 30. One inner fin 50 and the other inner fin 50 have the same structure, although they are arranged in different locations.

  Specifically, the inner fin 50 is an offset fin composed of straight portions 34 and 38 and an offset portion 39.

  The straight portion 34 is disposed upstream of the offset portion 39 in the refrigerant flow direction DRfw. The straight portion 38 is disposed downstream of the offset portion 39 in the refrigerant flow direction DRfw.

  The straight portion 34 constitutes fin channels 340a to 340h. The fin channels 340a to 340h are sequentially arranged from one side in the width direction DRw (upper side in FIG. 2) to the other side in the width direction DRw (lower side in FIG. 2).

  The straight portion 38 constitutes fin channels 350a to 350h. The fin channels 350a to 350h are sequentially arranged from one side in the width direction DRw (upper side in FIG. 2) to the other side in the width direction DRw.

In the offset portion 39, the upstream fin portions 31a to 31h and the downstream fin portions 32a to 32h are alternately arranged in the refrigerant flow direction DRfw to constitute an offset fin. Upstream fin portions 31a, 31b, 31c, and 31d , 31e, 31g, 31h are arranged in the tube width direction DRw.

  The upstream fin portions 31a, 31c, 31e, and 31g are each formed in a convex shape that is convex from one side to the other side in the tube stacking direction DRst. The upstream fin portions 31a, 31c, 31e, and 31g constitute fin channels 310a, 310c, 310e, and 310g, respectively.

  The upstream fin portions 31b, 31d, 31f, and 31h are each formed in a convex shape that is convex from the other side of the tube stacking direction DRst to the one side. The upstream fin portions 31b, 31d, 31f, and 31h constitute fin channels 310b, 310d, 310f, and 310h, respectively.

  The downstream fin portions 32a, 32b, 32c, 32d, 32e, 32g, and 32h are arranged in the tube width direction DRw, respectively. The downstream fin portions 32a, 32c, 32e, and 32g are each formed in a convex shape that is convex from one side to the other side in the tube stacking direction DRst. The downstream fin portions 32a, 32c, 32e, and 32g constitute fin channels 320a, 320c, 320e, and 320g, respectively.

  The downstream fin portions 32b, 32d, 32f, and 32h are each formed in a convex shape that is convex from the other side of the tube stacking direction DRst to the one side. The downstream fin portions 32b, 32d, 32f, and 32h constitute fin channels 320b, 320d, 320f, and 320h, respectively.

  The downstream fin portions 32a to 32h of the present embodiment configured as described above are offset from the corresponding upstream fin portion of the upstream fin portions 31a to 31h on the one side in the tube width direction DRw. Has been.

  As a result, the downstream fin portions 32a to 32h respectively correspond to the fin flow path formed by the corresponding upstream fin portion (hereinafter referred to as the corresponding upstream fin portion) of the upstream fin portions 31a to 31h and the corresponding upstream. A fin channel communicating with the fin channel adjacent to the side fin portion is configured.

  For example, the downstream fin part 32a is arranged offset to the corresponding upstream fin part 31a among the upstream fin parts 31a to 31h to one side in the tube width direction DRw. For this reason, the downstream fin portion 32a constitutes a fin channel 320a that communicates with the fin channel 310a formed by the corresponding upstream fin portion 31a and the fin channel 310b adjacent to the upstream fin portion 31a. Will do.

  Here, the direction in which the fin channels 340a to 340h and 350a to 350h are aligned corresponds to the tube width direction DRw. The direction in which the fin channels 310a to 310h and 320a to 320h are aligned corresponds to the tube width direction DRw. The direction in which the fin channels 310a to 310h, 320a to 320h, 340a to 340h, and 350a to 350h are aligned is a direction that intersects the refrigerant flow direction DRfw and that is along the contact surfaces 311 and 321 of the outer shell plates 31 and 32. .

  The inner fin 50 viewed from the tube stacking direction DRst has a rectangular shape as shown in FIG.

  A partition wall 341 is provided on one side of the inner fin 50 in the tube width direction DRw with respect to the fin channels 310a to 310h, 320a to 320h, 340a to 340h, and 350a to 350h.

  In addition, a partition wall 342 is provided on the other side of the tube width direction DRw with respect to the fin channels 310a to 310h, 320a to 320h, 340a to 340h, and 350a to 350h in the inner fin 50.

  As shown in FIGS. 2 and 3, the partition wall 341 of the inner fin 50 forms an end gap 302 as a first end gap between the inner wall surfaces 312 and 322 of the outer shell plates 31 and 32. ing.

  Similarly, the partition wall 342 forms an end gap 303 as a second end gap between the inner wall surfaces 312 and 322 of the outer shell plates 31 and 32. The partition wall 341 and the partition wall 342 are formed to extend in the refrigerant flow direction DRfw, similarly to the fin channels 310a to 310h, 320a to 320h, 340a to 340h, and 350a to 350h.

  As shown in FIG. 2, the heat exchange tube 3 includes a closing portion 40 and a closing portion 42 that are integrally formed with the outer shell plates 31 and 32. Since the outer shell plates 31 and 32 have the same structure as each other, in detail, one outer shell plate 31 includes a closing portion 40 and a closing portion 42, and the other outer shell plate 32 also includes the closing portion 40 and A blocking portion 42 is provided. For example, the closing portion 40 is shown in an enlarged manner in FIG.

  As shown in FIGS. 2 and 3, the closing portion 40 and the closing portion 42 are formed so as to protrude from the inner wall surfaces 312 and 322 of the outer shell plates 31 and 32, respectively. For example, the closing portion 40 and the closing portion 42 have rib shapes protruding from the inner wall surfaces 312 and 322, respectively.

  The closing part 40 closes the end gap 302. As a result, the closing portion 40 suppresses the refrigerant from flowing into the end gap 302. Similar to the end gap 302, the closing portion 42 closes the end gap 303. Thereby, the blocking part 42 suppresses the refrigerant from flowing into the end gap 303.

  As shown in FIG. 2, the closing portion 40 is disposed so as to fall within a range occupied by the straight portion 34 among the straight portions 34 and 38 and the offset portion 39 of the inner fin 50. The blocking portion 42 is disposed so as to fall within a range occupied by the straight portion 38 among the straight portions 34 and 38 and the offset portion 39 of the inner fin 50.

  Further, the closing portion 40 and the closing portion 42 are disposed so as to be out of the range occupied by the contact surfaces 311 and 321 of the outer shell plates 31 and 32.

  The straight portion 34 constitutes a plurality of partition walls 343 (seven partition walls 343 in FIG. 2) that partition the fin channels 340a to 340h. A partition 343 closest to the end gap 302 among the plurality of partitions 343 is defined as a partition 343a.

  The fin channels 340a and 340b are adjacent to each other with the partition wall 343a interposed therebetween. At the same time, the fin channel 340 a is adjacent to the end gap 302 via the partition wall 341.

  The fin channel 340a is the fin channel closest to the end gap 302 among the fin channels 340a to 340h. The fin channel 340b is the fin channel closest to the end gap 302 among the fin channels 340a to 340h.

  Of the plurality of partition walls 343a to 343h of the present embodiment, the partition wall 343a that separates the fin channels 340a and 340b on one side in the width direction DRw is configured to have an interval CR1 in the width direction DRw.

  This means that the closing portion 40 does not reach the partition wall 343a between the fin channels 301a and 301b on one side. Therefore, although the fin channel 301a on one side is partially deformed to the side where the channel cross-sectional area is narrowed by the closing portion 40, the fin channel 301b on one side is the side on which the channel cross-sectional area is narrowed. It has not been transformed into

  On the other hand, the straight portion 38 constitutes a plurality of partition walls 353 (seven partitions in FIG. 2) that partition the fin channels 350a to 350h. The fin channels 350h and 350g are adjacent to each other across the partition wall 353g. At the same time, the fin channel 350 h is adjacent to the end gap 303 via the partition wall 342.

  The fin channel 340 h is a fin channel closest to the end gap 303 among the plurality of fin channels 350 a to 350 h of the straight portion 38. The fin channel 350g is the fin channel closest to the end gap 303 among the plurality of fin channels 350a to 350h of the straight portion 38.

  Of the plurality of partition walls 353 of the present embodiment, the partition walls 353h that separate the fin channels 350h and 350g in the width direction DRw are configured to have an interval CR2 in the width direction DRw.

  As a result, the blocking portion 42 does not reach the partition wall 353g between the fin channels 350h and 350g on one side. Therefore, although the fin channel 350h on the other side is partially deformed to the side where the channel cross-sectional area is narrowed by the blocking portion 42, the seventh fin channel 350g on the other side has a narrow channel cross-sectional area. It is not deformed to the side to be.

  Returning to FIG. 1, the heat exchange tube 3 has cylindrical protruding pipe portions 35 that open in the tube stacking direction DRst and protrude in the tube stacking direction DRst on both sides of the tube longitudinal direction DRtb. The adjacent heat exchange tubes 3 are connected to each other by fitting the protruding tube portions 35 to each other and joining the side walls of the protruding tube portions 35 to each other.

  Of the plurality of heat exchange tubes 3, the heat exchange tubes 3 other than the pair of heat exchange tubes 3 positioned on the outermost side in the tube stacking direction DRst are provided on both surfaces of the opposing surfaces facing the adjacent heat exchange tubes 3. A pair of protruding tube portions 35 are provided. On the other hand, among the plurality of heat exchange tubes 3, the pair of heat exchange tubes 3 positioned on the outermost side in the tube stacking direction DRst are provided with the protruding pipe portions 35 only on one surface facing the adjacent heat exchange tubes 3. .

  Between the adjacent heat exchange tubes 3, the refrigerant flow paths 30 communicate with each other by joining the protruding pipe portions 35. Of the pair of protruding tube portions 35, one protruding tube portion 35 in the tube longitudinal direction DRtb functions as the supply header portion 11 in the stacked heat exchanger 1 by being connected to the tube stacking direction DRst. The supply header portion 11 is a portion for supplying the refrigerant to the refrigerant flow path 30 of each heat exchange tube 3. Moreover, the other protruding tube portion 35 in the tube longitudinal direction DRtb functions as the discharge header portion 12 in the stacked heat exchanger 1 by being connected in a plurality in the tube stacking direction DRst. The discharge header portion 12 is a portion for discharging the refrigerant from the refrigerant flow path 30 of each heat exchange tube 3.

  Further, the root portion 36 of the protruding tube portion 35 functions as an annular diaphragm. That is, when a compressive load is applied to the heat exchange tube 3 in the tube stacking direction DRst, the root portion 36 receives the compressive load via the projecting tube portion 35 toward the inside of the heat exchange tube 3. It is a deformed part to be deformed.

  Moreover, the refrigerant | coolant inlet tube 4 and the refrigerant | coolant derivation | leading-out pipe 5 are connected to one side of a pair of heat exchange tube 3 arrange | positioned among the several heat exchange tubes 3 in the tube lamination direction DRst. The refrigerant introduction pipe 4 is a refrigerant introduction part for introducing the refrigerant into the stacked heat exchanger 1. Therefore, the refrigerant introduction pipe 4 is connected to a portion constituting the supply header portion 11 of one of the pair of heat exchange tubes 3.

  On the other hand, the refrigerant lead-out pipe 5 is a refrigerant lead-out part for leading out the refrigerant from the stacked heat exchanger 1. Therefore, the refrigerant outlet pipe 5 is connected to a portion constituting the discharge header portion 12 of one of the pair of heat exchange tubes 3. The refrigerant introduction pipe 4 and the refrigerant outlet pipe 5 are joined to one of the pair of heat exchange tubes 3 arranged on the outermost side in the tube stacking direction DRst by a joining technique such as brazing.

  Here, the stacked heat exchanger 1 has the electronic component 2 disposed in a gap formed between the heat exchange tubes 3 in order to improve the adhesion between the electronic component 2 and the heat exchange tube 3. The electronic component 2 is sandwiched between both surfaces of the heat exchange tube 3 by being compressed in the tube stacking direction DRst by a press machine (not shown). At this time, the root portion 36 of the protruding tube portion 35 of the heat exchange tube 3 is deformed toward the inside of the heat exchange tube 3 by a compressive load. The compressive load is held by the press, so that the close contact between the electronic component 2 and the heat exchange tube 3 is maintained.

  Next, the manufacturing process of the laminated heat exchanger 1 will be briefly described. First, for each heat exchange tube 3, a pair of outer shell plates 31, 32, one intermediate plate 33, and two inner fins 50 are prepared. At this time, the closed portion 40 and the closed portion 42 are not yet formed on the outer shell plates 31 and 32.

  Subsequently, the heat exchange tube 3 is assembled from the outer shell plates 31 and 32, the intermediate plate 33, and the inner fins 50, and joined together by caulking, for example. Thereby, each heat exchange tube 3 which constitutes layered heat exchanger 1 is each assembled.

  When the crimping joining is completed, the closing portion 40 and the closing portion 42 are formed on the outer shell plates 31 and 32 by press working in each of the plurality of heat exchange tubes 3. At this time, the outer shell plates 31, 32, the intermediate plate 33, and the inner fin 50 are fixed by the caulking joining so as not to be displaced from each other by the press working.

  Specifically, the closing portion 40 and the closing portion 42 are press-molded so as to protrude from the inner wall surfaces 312 and 322 of the outer shell plates 31 and 32. In this press molding, the partition wall 341 of the inner fin 50 is molded so as to have a recessed shape along the blocking portion 40 at a portion included in the straight portion 34 a simultaneously with the molding of the closing portion 40. Therefore, after the molding, the partition wall 341 has a close contact surface 341 a that is in close contact with the closing portion 40.

  The same applies to the formation of the blocking portion 42. That is, the partition wall 342 of the inner fin 50 is molded so as to have a concave shape along the closed portion 42 at a portion included in the straight portion 34 c simultaneously with the molding of the closed portion 42. Therefore, after the molding, the partition wall 342 has a close contact surface that is in close contact with the closing portion 42.

  In the present embodiment, since the closing portion 40 is in close contact with the partition wall 341, the end gap 302 as a refrigerant flow path is completely closed after brazing and joining described later. Similarly, after the brazing and joining, the end gap 303 as the refrigerant flow path is completely closed by the closing portion 42.

  When the formation of the closing portion 40 and the closing portion 42 is completed, then, as shown in FIG. 1, the plurality of heat exchange tubes 3 are fitted together with the protruding tube portions 35 of the adjacent heat exchange tubes 3. They are stacked in the stacking direction DRst. The refrigerant introduction pipe 4 is connected to the supply header section 11, and the refrigerant outlet pipe 5 is connected to the discharge header section 12. Next, the laminated heat exchanger 1 is heated, and each component is brazed and joined.

  As described above, a compression load in the tube stacking direction DRst is applied to the laminated heat exchanger 1 completed by brazing and the laminated heat exchanger 1 is connected between the plurality of heat exchange tubes 3. The electronic component 2 is sandwiched between the two.

  Next, the flow of the refrigerant in the stacked heat exchanger 1 will be described. The refrigerant flows from the refrigerant introduction pipe 4 into the supply header portion 11 as indicated by an arrow FWWin in FIG. The refrigerant flowing into the supply header portion 11 is distributed from the supply header portion 11 to the refrigerant flow path 30 through the opening holes 33a of the plurality of heat exchange tubes 3.

  Here, the refrigerant flow path 30 includes the fin flow paths 340a to 340h, 310a to 310h, 320a to 320h, and 350a to 350h as described above.

  Therefore, the refrigerant flows through the plurality of fin channels 340a to 340h, and then the fin channels 310a to 310h, 320a to 320h → fin channels 310a to 310h → fin channels 320a to 320h → fin channels 310a to It flows in order of 310h-> fin channel 320a-320h-> fin channel 310a-310h-> fin channel 320a-320h-> ...-> fin channel 350a-350h.

  At this time, heat exchange is performed between the refrigerant and the electronic component 2 to cool the electronic component 2. At this time, the closing portion 40 prevents the refrigerant from flowing into the end gap 302 and the closing portion 42 prevents the refrigerant from flowing into the end gap 303. For example, as indicated by an arrow FL1 in FIG. 6A, the refrigerant flow going to the end gap 302 is prevented from flowing into the end gap 302 by the closing portion 40 and is directed to the fin channels 301a to 301i. Become.

  The refrigerant that has passed through the plurality of fin channels 301a to 301i in each of the heat exchange tubes 3 flows into the discharge header portion 12 of FIG. The refrigerant that has flowed into the discharge header portion 12 flows out to the refrigerant outlet pipe 5 as indicated by an arrow FWout.

  According to the present embodiment described above, the stacked heat exchanger 1 includes the plurality of heat exchange tubes 3 and the electronic components 2 such that the plurality of heat exchange tubes 3 and the electronic components 2 are alternately arranged in the stacking direction DRst. Are stacked.

  The stacked heat exchanger 1 is housed in each of a plurality of heat exchange tubes 3 and a plurality of heat exchange tubes 3 constituting a refrigerant flow path 30 for circulating a refrigerant that exchanges heat with the electronic component 2. Inner fins 50 that constitute the plurality of fin flow paths 310a to 310h and 320a to 320h that partition the respective refrigerant flow paths 30 and are arranged in the width direction are provided.

  The inner fin 50 includes upstream fin portions 31a to 31h and downstream fin portions 32a to 32h. The upstream fin portions 31a to 31h are arranged in the width direction DRw to form fin channels 310a to 310h. The downstream fin portions 32a to 32h are arranged in the width direction DRw on the downstream side of the refrigerant flow direction DRfw with respect to the upstream fin portions 31a to 31h to constitute the fin channels 320a to 320h.

  The downstream fin portions 32a to 32h are offset from the corresponding upstream fin portion of the upstream fin portions 31a to 31h on one side in the width direction DRw.

  The downstream fin portions 32a to 32h are fins communicating with the fin channel adjacent to the corresponding upstream fin portion of the upstream fin portions 31a to 31h and the fin channel formed by the corresponding upstream fin portion. Configure the flow path.

  The inner fin 50 is disposed on one side in the tube width direction DRw with respect to the fin channels 310 a to 310 h and 320 a to 320 h and between the inner walls 312 and 322 constituting the refrigerant channel 30 in the heat exchange tube 3. A partition wall 341 that forms an end gap 302 is provided.

  The partition wall 341 partitions the end gap 302 and the fin channels 310a to 310h and 320a to 320h. The stacked heat exchanger 1 includes a closing portion 40 that closes the end gap 302 and suppresses the refrigerant from flowing into the end gap 302.

  By the above, it can suppress that a refrigerant | coolant flows into the edge part clearance gap 302 from fin flow path 310a-310h, 320a-320h.

  The inner fin 50 is disposed on the other side in the tube width direction DRw with respect to the fin channels 310a to 310h and 320a to 320h, and between the inner walls 312 and 322 constituting the refrigerant channel 30 in the heat exchange tube 3. Are provided with a partition wall 342 that forms an end gap 303.

  The partition wall 342 partitions the end gap 303 and the fin channels 310a to 310h and 320a to 320h. The stacked heat exchanger 1 includes a closing portion 42 that closes the end gap 303 and prevents the refrigerant from flowing into the end gap 303.

  By the above, it can suppress that a refrigerant | coolant flows into the edge part clearance 303 from the fin flow paths 310a-310h and 320a-320h.

  Therefore, the refrigerant flow in the end gaps 302 and 303 can be sufficiently blocked.

  This will be described in detail using the proportionality shown in FIG. 6B. In the proportional laminated heat exchanger 1, as shown in FIG. 6B, the partition wall 341 is not provided. Except for this point, the proportional laminated heat exchanger 1 is the same as the laminated heat exchanger 1 of the present embodiment.

  First, if the partition wall 341 is not provided, in the heat exchange tube 3, most of the refrigerant that has passed through the fin channels 340a to 340h flows to the fin channels 320a to 320h, but passes through the fin channels 340a to 340h. A part of the refrigerant flows into the end gap 302 as indicated by an arrow FL2.

  For this reason, in comparison, the flow rate of the refrigerant flowing into the fin channels 320a to 320h is decreased by the amount of the refrigerant flowing into the end gap 302. And since the edge part clearance gap 302 is located in the end of the tube width direction DRw in the heat exchange tube 3, the refrigerant | coolant in the edge part clearance gap 302 is compared with the refrigerant | coolant which flows through the fin flow paths 320a-320h. However, it is difficult to exchange heat with the electronic component 2 sandwiched between the heat exchange tubes 3. The same applies to the end gap 303.

  Therefore, in this embodiment, by providing the closing portions 40 and 42 in the heat exchange tube 3, it is possible to prevent the refrigerant from flowing through the end gap 302 and the end gap 303. It is possible to improve the heat exchange performance.

  In the present embodiment, the inner fin 50 constitutes the partition walls 341 and 342. For this reason, compared with the case where the partition walls 341 and 342 are provided independently with respect to the inner fin 50, the number of parts can be reduced.

  In the present embodiment, the closing portions 40 and 42 are configured by deforming the outer shell plates 31 and 32. For this reason, the number of parts can be reduced as compared with the case where the closing portions 40 and 42 are provided for the outer shell plates 31 and 32.

  As described above, when the partition walls 341 and 342 and the closing portions 40 and 42 are added, an increase in the number of parts can be suppressed.

(Second Embodiment)
In the second embodiment, an example in which a wavy offset fin that causes the plurality of fin channels to meander in the width direction in the offset portion 39 of the inner fin 50 in the first embodiment will be described with reference to FIG. 7A. To do.

  The stacked heat exchanger 1 of the present embodiment and the stacked heat exchanger 1 of the first embodiment are the same except for the offset portions 39 of the inner fins 50. For this reason, below, the offset part 39 of the inner fin 50 of the laminated heat exchanger 1 of this embodiment is demonstrated.

  The upstream fin portions 31a to 31h are configured such that the fin flow paths 310a to 310h are directed from one side in the width direction to the other side in the width direction as they proceed from the upstream side to the downstream side in the refrigerant flow direction DRfw.

  The downstream fin portions 32a to 32h are configured such that the fin flow paths 320a to 320h are directed from the other side in the width direction toward the one side in the width direction as they proceed from the upstream side in the refrigerant flow direction DRfw to the downstream side.

  The upstream fin portion 31a includes upstream side walls 311a to 311h (only 311a to 311d are shown in FIG. 7A) that partition the fin channels 310a to 310h. The downstream fin portion 32a includes downstream side walls 321a to 321h (only 321a to 321d are shown in FIG. 7A) that partition the fin channels 320a to 320h.

  In the present embodiment, the inner fin 50 includes partition walls 341 and 342 as in the first embodiment.

  The partition wall 341 includes a plurality of upstream side walls 311a and a plurality of downstream side walls 321a. The upstream side wall 311a is an upstream side wall located on the one side in the width direction DRw among the upstream side walls 311a to 310h. The downstream side wall 321a is the downstream side wall located on the one side in the width direction DRw among the downstream side walls 321a to 320h.

  The refrigerant flow direction DRfw downstream end of the upstream side wall 311a and the refrigerant flow direction DRfw upstream end of the downstream side wall 321a are connected. A refrigerant flow direction DRfw upstream end of the upstream side wall 311a and a refrigerant flow direction DRfw downstream end of the downstream side wall 321a are connected.

  The partition wall 342 includes a plurality of upstream side walls 311h and a plurality of downstream side walls 321h. The refrigerant flow direction DRfw downstream end of the upstream side wall 311h and the refrigerant flow direction DRfw upstream end of the downstream side wall 321h are connected. The upstream end portion in the refrigerant flow direction DRfw in the upstream side wall 311h and the downstream end portion in the refrigerant flow direction DRfw in the downstream side wall 321h are connected.

  In the present embodiment configured as described above, the upstream fin portions 31a to 31h and the downstream fin portions 32a to 32h are alternately arranged one by one in the refrigerant flow direction DRfw, whereby fin channels 310a to 310h, 320a to 320h are configured in a wave shape.

  The downstream fin portions 32a to 32h are offset from the corresponding upstream fin portions of the upstream fin portions 31a to 31h in the width direction DRw, respectively. Each of the downstream fin portions 32a to 32h communicates with a fin passage formed by the corresponding upstream fin portion and a fin passage adjacent to the corresponding upstream fin portion.

  On the other hand, as shown in FIG. 7B, in the heat exchange tube 3 of the proportional laminated heat exchanger 1 in which the partition wall 341 is not provided, most of the refrigerant that has passed through the fin channels 340a to 340h is the fin channel. It flows to 320a-320h. On the other hand, a part of the refrigerant that has passed through the fin channels 340a to 340h flows into the end gap 302 as indicated by an arrow FL3. For this reason, in comparison, the flow rate of the refrigerant flowing into the fin channels 320a to 320h is decreased by the amount of the refrigerant flowing into the end gap 302.

  On the other hand, the stacked heat exchanger 1 of the present embodiment suppresses the refrigerant from flowing from the fin channels 310a to 310h and 320a to 320h into the end gap 302 in substantially the same manner as in the first embodiment. A partition wall 341 to be closed, and a closing portion 40 that closes the end gap 302 and prevents the refrigerant from flowing into the end gap 302. Accordingly, it is possible to sufficiently block the refrigerant flow in the end gap 302.

  On the other hand, the stacked heat exchanger 1 closes the end gap 303 by closing the end gap 303 and the partition wall 342 for suppressing the refrigerant from flowing from the fin channels 310 a to 310 h and 320 a to 320 h into the end gap 303. And a closing portion 42 that suppresses the flow of the refrigerant. Accordingly, it is possible to sufficiently block the refrigerant flow in the end gap 303.

(Third embodiment)
In the said 2nd Embodiment, although the upstream side wall 311a and the downstream side wall 321a were connected and the example which comprised the partition wall 341 was demonstrated, it replaced with this, In this 3rd Embodiment, several as follows. A partition wall 341 is constituted by the upstream side wall 311a and the plurality of downstream side walls 321a.

  The present embodiment and the second embodiment are the same in other configurations except that the partition walls 341 and 342 are different from each other. For this reason, hereinafter, the partition walls 341 and 342 of the present embodiment will be described, and description of other configurations will be omitted.

  In the partition wall 341 of the present embodiment, the refrigerant flow direction DRfw upstream end 400 of the downstream side wall 321a is offset to the width direction DRw one side of the upstream side wall 311a with respect to the refrigerant flow direction DRfw downstream end 401. ing. Therefore, a gap 410 is formed between the refrigerant flow direction DRfw upstream end 400 of the downstream side wall 321a and the refrigerant flow direction DRfw downstream end 401 of the upstream side wall 311a.

  However, the refrigerant that has passed through the fin channel 340a flows toward the other side in the width direction DRw along the upstream side wall 311a. For this reason, the refrigerant does not flow from the fin channel 340 a to the end gap 302 through the gap 410.

  In the partition wall 341 of the present embodiment, the refrigerant flow direction DRfw downstream end 402 of the downstream side wall 321a is connected to the refrigerant flow direction DRfw upstream end 403 of the upstream side wall 311a.

  For this reason, the refrigerant flowing along the downstream side wall 321a continues to flow along the upstream side wall 311a. For this reason, the refrigerant in the fin channel 340a flows along the downstream side wall 321a and the upstream side wall 311a. For this reason, even if a gap 410 is formed between the refrigerant flow direction DRfw upstream end 400 of the downstream side wall 321a and the refrigerant flow direction DRfw downstream end 401 of the upstream side wall 311a, the fin channel 340a The refrigerant does not flow into the end gap 302 through the gap 410.

  As described above, even if the gap 410 is formed between the downstream side wall 321a and the upstream side wall 311a, the partition wall 341 is connected to the end portions of the fin channels 310a to 310h and 320a to 320h in the same manner as in the first embodiment. The role which suppresses a refrigerant | coolant flowing into the clearance gap 302 can be played.

  On the other hand, in the partition wall 342 of the present embodiment, the refrigerant flow direction DRfw upstream end 420 of the downstream side wall 321h is on the one side in the width direction DRw of the upstream side wall 311h with respect to the refrigerant flow direction DRfw downstream end 421. It is offset. Therefore, a gap 430 is formed between the refrigerant flow direction DRfw upstream end 420 of the downstream side wall 321h and the refrigerant flow direction DRfw downstream end 421 of the upstream side wall 311h.

  However, the refrigerant that has passed through the fin channel 340h flows toward the one side in the width direction DRw along the upstream side wall 311h. For this reason, the refrigerant does not flow from the fin channel 340h to the end gap 303 through the gap 430.

  In the partition wall 342 of the present embodiment, the downstream end 422 in the refrigerant flow direction DRfw in the downstream side wall 321h is connected to the upstream end 423 in the refrigerant flow direction DRfw in the upstream side wall 311h.

  For this reason, the refrigerant flowing along the downstream side wall 321h continues to flow along the upstream side wall 311h. For this reason, the refrigerant in the fin channel 340h flows along the downstream side wall 321h and the upstream side wall 311h. For this reason, even if a gap 430 is formed between the refrigerant flow direction DRfw upstream end 422 of the downstream side wall 321h and the refrigerant flow direction DRfw downstream end 423 of the upstream side wall 311h, the fin channel 340h The refrigerant does not flow into the end gap 303 through the gap 430.

  As described above, even if the gap 430 is formed between the downstream side wall 321h and the upstream side wall 311h, the partition wall 342 is connected to the end portions from the fin channels 310a to 310h and 320a to 320h in the same manner as in the first embodiment. It can play a role of suppressing the flow of the refrigerant in the gap 303.

(Other embodiments)
(1) In the first to third embodiments, the example in which the heat exchange target is cooled by heat exchange between the refrigerant and the heat exchange target has been described, but instead, the refrigerant and the heat exchange target. The object to be heat exchanged may be heated by heat exchange between the two.

  (2) In the first to third embodiments, the example in which the electronic component 2 is used as the heat exchange target has been described. However, instead of this, an apparatus other than the electronic component 2 and a fluid (liquid, gas) are covered. You may use as a heat exchange object.

  (3) In the first to third embodiments, the example in which the closing portions 40 and 42 are configured by the outer shell plates 31 and 32 has been described. However, the present invention is not limited thereto, and is independent of the outer shell plates 31 and 32. The blocking portions 40 and 42 may be configured.

  (4) In the first to third embodiments, the example in which the partition walls 341 and 342 are configured by the inner fins has been described. Instead, the partition walls 341 and 342 are configured independently of the inner fins. May be.

  (5) It should be noted that the present invention is not limited to the above-described embodiment, and can be appropriately changed within the scope described in the claims. Further, the above embodiments are not irrelevant to each other, and can be combined as appropriate unless the combination is clearly impossible. In each of the above-described embodiments, it is needless to say that elements constituting the embodiment are not necessarily indispensable except for the case where it is clearly indicated that the element is essential and the case where the element is clearly considered essential in principle. Yes. Further, in each of the above embodiments, when numerical values such as the number, numerical value, quantity, range, etc. of the constituent elements of the embodiment are mentioned, it is clearly limited to a specific number when clearly indicated as essential and in principle. The number is not limited to the specific number except for the case. Further, in each of the above embodiments, when referring to the shape, positional relationship, etc. of the component, etc., the shape, unless otherwise specified and in principle limited to a specific shape, positional relationship, etc. It is not limited to the positional relationship or the like.

(Summary)
According to the first aspect described in the first to third embodiments and part or all of the other embodiments, the refrigerant flow path for circulating the refrigerant that exchanges heat with the heat exchange target. Laminated heat comprising a plurality of constituting heat exchange tubes (3), wherein the plurality of heat exchange tubes and the heat exchange object are laminated so that the heat exchange tubes and the heat exchange object are alternately arranged in the lamination direction. An exchanger comprising inner fins housed in each of the plurality of heat exchange tubes, the inner fins being arranged in the width direction and having an upstream fin channel for circulating the refrigerant in the refrigerant channel. A plurality of upstream fin portions that are respectively configured and arranged in the width direction on the downstream side in the refrigerant flow direction with respect to the plurality of upstream fin portions, and corresponding upstream fin portions among the plurality of upstream fin portions Offset in the width direction And a plurality of downstream fin portions that respectively constitute downstream fin passages for allowing the refrigerant to flow through the refrigerant passages. A first end clearance between the upstream fin channel and the downstream fin channel is disposed on one side in the width direction of the heat exchange tube and the inner wall of the refrigerant channel. And a first closing portion that closes the first end portion gap and prevents the refrigerant from flowing into the first end portion gap.

  Therefore, it is possible to suppress the refrigerant from flowing from the fin channel to the first end gap.

  According to the second aspect, the refrigerant flow path that is disposed on the other side in the width direction with respect to the respective upstream fin flow paths and the respective downstream fin flow paths of the heat exchange tubes and constitutes the heat exchange tubes. A second partition wall that forms a second end gap between the inner wall and the second wall, and a second closing portion that blocks the second end gap and prevents the refrigerant from flowing into the second end gap. .

  Therefore, it is possible to suppress the refrigerant from flowing from the fin channel to the second end gap.

  According to the third aspect, the plurality of upstream fin portions and the plurality of downstream fin portions are formed to circulate the refrigerant in a wavy shape that meanders in the width direction.

  According to the fourth aspect, each of the plurality of upstream fin portions is formed such that the fin channel is directed from one side in the width direction to the other side in the width direction as it proceeds from the upstream side to the downstream side in the refrigerant flow direction. Each of the plurality of downstream fin portions is formed such that the fin flow path is directed from the other side in the width direction toward the one side in the width direction as it proceeds from the upstream side in the refrigerant flow direction to the downstream side. By alternately arranging the portions and the plurality of downstream fin portions one by one in the refrigerant flow direction, the refrigerant is circulated in a wavy shape that meanders in the width direction.

  According to the fifth aspect, the heat exchange tube and the heat exchange target are alternately stacked, including a plurality of heat exchange tubes constituting a refrigerant flow path for circulating the refrigerant that exchanges heat with the heat exchange target. A stacked heat exchanger in which a plurality of heat exchange tubes and a heat exchange target are stacked so as to be lined up in a direction, and includes inner fins housed in each of the plurality of heat exchange tubes. A plurality of upstream fin passages that are arranged in the width direction and that respectively constitute upstream fin passages that allow the refrigerant to flow through the refrigerant passages, and downstream of the plurality of upstream fin portions in the refrigerant flow direction. The downstream fin flow is arranged in the width direction and is offset in the width direction with respect to the corresponding upstream fin portion among the plurality of upstream fin portions, and further distributes the refrigerant in the refrigerant flow path. Each way A plurality of downstream fin portions formed, and the plurality of upstream fin portions and the plurality of downstream fin portions are alternately arranged one by one in the refrigerant flow direction, thereby causing the refrigerant to meander in the width direction. It is an offset fin to be circulated, and the upstream fin portion disposed on one side in the width direction among the plurality of upstream fin portions is formed between the inner wall constituting the refrigerant flow path and the upstream fin flow path of the heat exchange tube. A downstream fin portion provided with a first upstream side wall for partitioning and disposed on one side in the width direction among the plurality of downstream fin portions is configured to partition between the inner wall of the heat exchange tube and the downstream fin flow path. 1 downstream side wall is provided, and the upstream end portion in the refrigerant flow direction of the first downstream side wall is arranged to be offset to one side in the width direction with respect to the downstream end portion in the refrigerant flow direction in the first upstream fin portion. 1st downstream side Among the first upstream fins, the downstream end in the refrigerant flow direction is connected to the upstream end in the refrigerant flow direction, and the stacked heat exchanger includes the first upstream side wall and the first downstream side wall. And a first closing portion that blocks a first end gap formed between the heat exchange tube and an inner wall constituting the refrigerant flow path, and suppresses the refrigerant from flowing into the first end gap.

  Therefore, it is possible to suppress the refrigerant from flowing from the fin channel to the first end gap.

  According to the sixth aspect, the upstream fin portion arranged on the other side in the width direction among the plurality of upstream fin portions is the second upstream partitioning the inner wall of the heat exchange tube and the upstream fin flow path. The downstream fin portion that includes the side wall and is disposed on the other side in the width direction among the plurality of downstream fin portions includes a second downstream side wall that partitions between the inner wall of the heat exchange tube and the downstream fin flow path, Of the second downstream side wall, the upstream end portion in the refrigerant flow direction is disposed so as to be offset to one side in the width direction with respect to the downstream end portion in the refrigerant flow direction in the second upstream fin portion. The downstream end in the refrigerant flow direction in the side wall is connected to the upstream end in the refrigerant flow direction in the second upstream fin portion, and the stacked heat exchanger includes the second upstream side wall and the second downstream side. Inner wall constituting the refrigerant flow path constituting the side wall and the heat exchange tube A second closing portion suppresses the flow of refrigerant to the second end gap to close the second end gap formed between the.

  Therefore, it is possible to suppress the refrigerant from flowing from the fin channel to the second end gap.

1 Stack heat exchanger 2 Electronic component (Heat exchange target)
3 Heat exchange tubes 31, 32 Outer shell plate 33 Intermediate plate 34 Inner fin 36 Offset portion 31a to 31h Upstream fin portion 32a to 32h Downstream fin portion 310a to 310h Fin flow path

Claims (6)

The heat exchange tube (3) includes a plurality of heat exchange tubes (3) that constitute a refrigerant flow path (30) for circulating a refrigerant that exchanges heat with the heat exchange target (2), and the heat exchange tube and the heat exchange target are A stack-type heat exchanger in which the plurality of heat exchange tubes and the heat exchange target are stacked so as to be alternately arranged in the stacking direction,
An inner fin (34) accommodated in each of the plurality of heat exchange tubes;
The inner fin is
A plurality of upstream fin portions (31a to 31h) that are arranged in the width direction and that respectively constitute upstream fin channels (310a to 310h) through which the refrigerant flows in the refrigerant channel;
Aligned in the width direction on the downstream side in the refrigerant flow direction with respect to the plurality of upstream fin portions, and provided offset in the width direction with respect to the corresponding upstream fin portion among the plurality of upstream fin portions. A plurality of downstream fin portions (32a to 32h) that respectively constitute downstream fin channels (320a to 320h) for circulating the refrigerant in the refrigerant channel,
The laminated heat exchanger is
An inner wall of the heat exchange tube that is disposed on one side in the width direction with respect to the respective upstream fin channel and the respective downstream fin channel, and constitutes the refrigerant channel in the heat exchange tube. A first partition wall (341) that forms a first end gap (302) with (312, 322);
A laminated heat exchanger comprising: a first closing portion (40) that closes the first end portion gap and suppresses a refrigerant from flowing into the first end portion gap. Among the heat exchange tubes, the refrigerant flow passages that are disposed on the other side in the width direction with respect to the respective upstream fin passages and the respective downstream fin passages constitute the heat exchange tubes. A second partition wall (342) that forms a second end gap (303) between the inner wall (312, 322);
2. The stacked heat exchanger according to claim 1, further comprising a second closing portion (42) that closes the second end portion gap and suppresses the refrigerant from flowing into the second end portion gap.   The stacked heat exchanger according to claim 1 or 2, wherein the plurality of upstream fin portions and the plurality of downstream fin portions are formed so as to circulate the refrigerant in a wavy shape that meanders in the width direction. . Each of the plurality of upstream fin portions is formed such that the fin flow path is directed from one side in the width direction toward the other side in the width direction as it proceeds from the upstream side to the downstream side in the refrigerant flow direction.
Each of the plurality of downstream fin portions is formed such that the fin flow path is directed from the other side in the width direction toward one side in the width direction as it proceeds from the upstream side to the downstream side in the refrigerant flow direction.
The plurality of upstream fin portions and the plurality of downstream fin portions are alternately arranged one by one in the refrigerant flow direction, so that the refrigerant circulates in a wave shape that meanders in the width direction. Laminated heat exchanger. The heat exchange tube (3) includes a plurality of heat exchange tubes (3) that constitute a refrigerant flow path (30) through which a refrigerant that exchanges heat with the heat exchange target (2) is provided. A stack-type heat exchanger in which the plurality of heat exchange tubes and the heat exchange target are stacked so as to be alternately arranged in the stacking direction,
An inner fin (34) accommodated in each of the plurality of heat exchange tubes;
The inner fin is
A plurality of upstream fin portions (31a to 31h) that are arranged in the width direction and that respectively constitute upstream fin channels (310a to 310h) through which the refrigerant flows in the refrigerant channel;
Aligned in the width direction on the downstream side in the refrigerant flow direction with respect to the plurality of upstream fin portions, and provided offset in the width direction with respect to the corresponding upstream fin portion among the plurality of upstream fin portions. And a plurality of downstream fin portions (32a to 32h) that respectively constitute downstream fin channels (320a to 320h) for circulating the refrigerant in the refrigerant channel, and the plurality of upstream fins. Part and the plurality of downstream fin portions are alternately arranged in the refrigerant flow direction one by one, thereby offset fins that circulate in a wavy shape causing the refrigerant to meander in the width direction,
Among the plurality of upstream fin portions, the upstream fin portion (31a) arranged on one side in the width direction is configured to connect the inner wall (312 and 322) constituting the refrigerant flow path and the upstream of the heat exchange tube. A first upstream side wall (311a) that partitions the side fin channel,
The downstream fin portion (32a) disposed on one side in the width direction among the plurality of downstream fin portions is a first downstream side wall that partitions between the inner wall of the heat exchange tube and the downstream fin flow path. (321a)
The refrigerant flow direction upstream end portion (400) of the first downstream side wall is offset to one side in the width direction with respect to the refrigerant flow direction downstream end portion (401) of the first upstream fin portion. Has been placed,
The downstream end portion (403) in the refrigerant flow direction of the first downstream side wall is connected to the upstream end portion (402) in the refrigerant flow direction of the first upstream fin portion,
The laminated heat exchanger is
A first end gap (302) formed between the first upstream side wall and the first downstream side wall and the inner walls (312 and 322) constituting the refrigerant flow path in the heat exchange tube is closed. A stacked heat exchanger comprising a first closing portion (40) for suppressing a refrigerant from flowing into the first end gap. The upstream fin portion (31h) arranged on the other side in the width direction among the plurality of upstream fin portions is a second upstream partitioning the inner wall of the heat exchange tube and the upstream fin flow path. With side walls (311h),
The downstream fin portion (32h) arranged on the other side in the width direction among the plurality of downstream fin portions is a second downstream side wall that partitions between the inner wall of the heat exchange tube and the downstream fin flow path. (321h)
The refrigerant flow direction upstream end portion (420) of the second downstream side wall is offset to one side in the width direction with respect to the refrigerant flow direction downstream end portion (421) of the second upstream fin portion. Has been placed,
The downstream end portion (422) in the refrigerant flow direction of the second downstream side wall is connected to the upstream end portion (423) in the refrigerant flow direction of the second upstream fin portion,
The laminated heat exchanger is
A second end gap (303) formed between the second upstream side wall and the second downstream side wall and the inner walls (312 and 322) constituting the refrigerant flow path constituting the heat exchange tube is closed. The stacked heat exchanger according to claim 5, further comprising a second closing portion (42) that suppresses the refrigerant from flowing into the second end portion gap.

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