JP2019211161A - Heat exchanger - Google Patents

Abstract

To improve durability of a heat exchanger.SOLUTION: A heat exchanger 100 includes: multiple tubes 9 in which a coolant (a second fluid) circulates; support plates 11 supporting end parts 9a of the multiple tubes 9 laminated; and passage plates 31 forming passages, in which intake air (a first fluid) circulates, between the tubes 9. The passage plate 31 has: a supported plate part 34b joined to the support plate 11; a passage opening part 35 which opens in the supported plate part 34b and in which the intake air circulates; and passage plate cutout parts 36 which are formed continuing into the passage opening part 35 and formed by cutting out the supported plate part 34b.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a heat exchanger in which heat is exchanged between fluids.

  Patent Document 1 discloses a heat exchanger (intercooler) that cools a first fluid (intake air) with a second fluid (engine coolant).

  The heat exchanger described in Patent Document 1 includes a plurality of tubes to be stacked, a core plate that supports each of the stacked tubes, and a flow path that is disposed so as to cover each tube and through which the first fluid flows. A member. The end portion of each tube is joined to the core plate, and the flow path forming member is joined to the core plate.

JP 2014-214955 A

  In the heat exchanger described in Patent Document 1, thermal distortion occurs at the ends of the core plate and the tube due to the difference in thermal expansion between the tube and the flow path forming member. The thermal strain generated at the end of the tube formed by the thin material becomes a factor that reduces the durability of the heat exchanger.

  This invention is made | formed in view of said problem, and aims at improving the durability of a heat exchanger.

  According to an aspect of the present invention, there is provided a heat exchanger in which heat is exchanged between the first fluid and the second fluid, and the plurality of tubes stacked with the plurality of tubes through which the second fluid flows. A support plate that supports an end of the tube, and a flow path plate that forms a flow path through which the first fluid flows between the tubes, and the flow path plate is bonded to the support plate. A support plate, a channel opening that opens to the supported plate and through which the first fluid flows, and a channel plate notch that is formed continuously with the channel opening and cuts the supported plate And a heat exchanger characterized by comprising:

  According to an aspect of the present invention, the heat exchanger performs heat exchange between the first fluid and the second fluid, and includes a plurality of tubes through which the second fluid flows, and the first fluid inside. Forming a flow path through which the gas flows, the case having a pair of support plates that support the ends of the plurality of tubes to be stacked, and a rectangular flow path opening through which the first fluid flows. A flow path plate having a flow path plate notch formed in a longitudinal direction of the tube from a corner of the flow path opening, the both ends of the flow path plate being joined to the support plate. There is provided a heat exchanger characterized by comprising:

  According to the above aspect, the flow path plate is urged to be deformed due to a difference in thermal expansion amount generated between the flow path plate and the tube due to a decrease in rigidity due to the flow path plate notch. Thereby, the thermal distortion which arises in the edge part of a tube is suppressed small, and durability of a heat exchanger is improved.

FIG. 1 is a perspective view showing a heat exchanger according to an embodiment of the present invention. FIG. 2 is a perspective view showing a state in which the heat exchanger is disassembled. FIG. 3 is a perspective view showing the assembly of the heat exchanger. 4A, 4B, and 4C are a front view, a plan view, and a side view, respectively, showing a support plate. 5A, 5B, and 5C are a side view, a front view, and a plan view, respectively, showing a flow path plate. FIG. 6A is a cross-sectional view showing a state before the heat exchanger is thermally deformed. FIG. 6B is a cross-sectional view showing a state in which the heat exchanger is thermally deformed. FIG. 7 is a perspective view showing a state in which the heat exchanger is thermally deformed.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  FIG. 1 is a perspective view showing a heat exchanger 100 according to the present embodiment. The heat exchanger 100 includes a first flow path 1 through which intake air (first fluid) flows, and a second flow path 2 through which coolant (second fluid) circulates. The heat exchanger 100 is mounted on a vehicle (not shown), and is used as a water-cooled charge air cooler that cools intake air supercharged to an engine (not shown) with a coolant. The coolant flows through the heat exchanger 100 and then flows through a radiator (not shown) to radiate heat to the outside air.

  FIG. 2 is a perspective view showing a state in which the heat exchanger 100 is disassembled. The heat exchanger 100 includes a case 20 and ducts 6 and 7 that form the first flow path 1, and a plurality of tubes 9 and tanks 4 and 5 that form the second flow path 2.

  The plurality of tubes 9 are stacked in four rows. Fins 8 are disposed between the layers of the tube 9. The tubes 9 and the fins 8 stacked on each other constitute the core 3 in which heat exchange is performed between the intake air and the coolant. The core 3 is not limited to the above-described configuration, and may be configured only by the tubes 9 that are not provided with the fins 8 and are stacked on each other.

  The case 20 includes a pair of support plates 11 joined to both ends 9 a of each tube 9, a pair of stacked end plates 21 disposed at both ends in the stacking direction of the tubes 9, and a flow path orthogonal to each tube 9. And a pair of flow path plates 31 disposed at both ends in the direction. The case 20 is not limited to the above configuration, and the laminated end plate 21 and the flow path plate 31 may be integrally formed.

  Each support plate 11 is joined to tanks 4 and 5 for guiding the coolant to each tube 9. One tank 4 is joined with a pipe 18 through which the cooling liquid flows in and a pipe 19 through which the cooling liquid flows out.

  FIG. 3 is a perspective view showing the assembly 10 in which the members of the heat exchanger 100 are assembled. The metal assembly 10 is transferred to a heating furnace and subjected to heat treatment, whereby each joint is joined by brazing.

  As shown in FIGS. 1 and 2, ducts 6 and 7 that guide intake air are connected to each flow path plate 31 of the assembly 10. As will be described later, the resin ducts 6 and 7 are caulked and fixed to each flow path plate 31. As shown in FIG. 2, a packing 40 is disposed between the ducts 6 and 7 and each flow path plate 31.

  When the heat exchanger 100 is operated, the coolant is distributed from the pipe 18 to the tubes 9 in the two upstream rows through the distribution chamber (not shown) in the tank 4 as shown by the black arrows in FIG. The coolant flowing through the upstream two rows of tubes 9 is changed in flow direction in the other tank 5 and distributed to the downstream two rows of tubes 9. The coolant that has passed through the tubes 9 in the two downstream rows gathers in a collecting chamber (not shown) in the tank 4 and flows out from the pipe 19 and circulates.

  On the other hand, the intake air flows into the core 3 through one duct 6 and the flow path plate 31 and is distributed to the first flow path 1 between the tubes 9 as indicated by white arrows in FIG. The intake air flowing through the first flow path 1 between the tubes 9 is cooled by dissipating heat to the coolant flowing through the tubes 9. The intake air flowing out from the first flow path 1 between the tubes 9 gathers through the other flow path plate 31 and the duct 7 and is supplied to a combustion chamber (not shown) of the engine.

  Hereinafter, the structure of the heat exchanger 100 will be described by setting three axes X, Y, and Z orthogonal to each other in each drawing. In the core 3, the flow path direction in which the intake air flows through the first flow path 1 between the tubes 9 is referred to as “X-axis direction”, and the tube longitudinal direction in which the tube 9 extends is referred to as “Y-axis direction”. The stacking direction in which the tubes 9 are stacked is referred to as the “Z-axis direction”.

  As shown in FIG. 2, the tube 9 has a flat cylindrical shape extending in the X-axis direction and the Y-axis direction. The tube 9 is formed by press-molding a metal plate having a plate thickness t1. The shape of the tube 9 is not limited to this, and may be any shape such as a pipe having a circular cross section.

  Each tube 9 is supported at both ends by a pair of support plates 11.

  4A, 4B, and 4C are a front view, a plan view, and a side view showing the support plate 11, respectively. The box-shaped support plate 11 includes a side plate portion 12 extending in the X-axis direction and the Z-axis direction, a pair of laminated end plate portions 13 extending in the X-axis direction and the Y-axis direction, and the Y-axis direction and the Z-axis. And a pair of flow path end plate portions 14 extending in the direction. The laminated end plate portion 13 and the flow path end plate portion 14 are formed in a rectangular frame shape connected to the four sides of the side plate portion 12.

  The support plate 11 is formed by press-molding a metal plate. The support plate 11 is formed of a metal plate having a plate thickness t2 larger than the plate thickness t1 of the tube 9.

  In the substantially rectangular side plate portion 12, a plurality of burring holes 12a are opened in four rows. The burring hole 12a opens to the burring portion 12b protruding from the side plate portion 12 in the Y-axis direction. End portions 9a (see FIGS. 2 and 6A) of the respective tubes 9 are inserted and joined to the respective burring holes 12a.

  As shown in FIG. 4C, the flow channel end plate portion 14 has a bonding plate portion 14a to which the flow channel plate 31 is bonded. The joining plate portion 14 a has an opening 15 that opens toward the first flow path 1. The opening 15 has two corners 15a arranged in the Z-axis direction.

  As shown in FIG. 4C, the support plate 11 has a pair of support plate cutouts 16 that open to two corners 15a. Each support plate cutout portion 16 is formed by cutting out the joining plate portion 14 a and has a concave shape formed in the Y-axis direction from the opening 15.

  FIGS. 5A, 5 </ b> B, and 5 </ b> C are a side view, a plan view, and a front view, respectively, showing the flow path plate 31. The flow path plate 31 includes a frame portion 34 having a substantially rectangular outer shape, a pair of side end caulking plate portions 32 and a pair of stacked end caulking plate portions 33 connected to the four sides of the frame portion 34.

  The flow path plate 31 is formed by press-molding a metal plate. The flow path plate 31 is formed of a metal plate having a plate thickness t3 larger than the plate thickness t2 of the support plate 11 (see FIG. 6A).

  As shown in FIG. 5A, the frame part 34 includes a pair of supported plate parts 34a extending in the Y-axis direction and the Z-axis direction, and a pair of supported parts extending in the X-axis direction and the Z-axis direction. A plate portion 34b. The laminated end plate 21 is joined to the supported plate portion 34a. As will be described later, the support plate 11 is joined to the supported plate portion 34b.

  The frame portion 34 has a beam portion 34c that connects the central portions of the supported plate portions 34a. However, the present invention is not limited thereto, and the frame portion 34 may not have the beam portion 34c.

  The frame portion 34 includes a substantially rectangular channel opening 35 that opens to face the first channel 1, and two pairs of channel plate cutouts 36 that open to the channel opening 35. Each flow path plate notch 36 is formed by notching the supported plate 34b.

  The flow path opening 35 includes a pair of opening ends 35a extending in the Y-axis direction, a pair of opening ends 35b extending in the Z-axis direction, and four corners at which the opening ends 35a and the opening ends 35b intersect. 35c.

  Each flow path plate notch 36 is disposed at each of the four corners 35c and is formed to be continuous with each open end 35a.

  Each flow path plate notch 36 is formed in a concave shape in the Y-axis direction from the opening end 35b.

  Each flow path plate notch 36 is arranged at substantially the same position as the support plate notch 16 of the support plate 11, so that it matches the support plate notch 16.

  FIG. 6A is a cross-sectional view showing a joint portion of the support plate 11, the flow path plate 31 and the tank 4. Tanks 4 and 5 are joined to the outer surface of the side plate portion 12 of the support plate 11. The side plate portion 12 functions as a partition wall that partitions the second flow path 2 in the tanks 4 and 5 and the first flow path 1 between the tubes 9.

  As shown in FIG. 6A, the supported plate portion 34 b of the flow path plate 31 is bonded to the outer surface of the bonding plate portion 14 a of the support plate 11.

  FIG. 6A shows a state in which the duct 7 is attached to the flow path plate 31. The flow path plate 31 is assembled so that the open ends of the ducts 6 and 7 are in contact with the outer surface of the frame portion 34 via the packing 40. The side end crimping plate portion 32 and the stacked end crimping plate portion 33 are raised so as to be substantially orthogonal to the frame portion 34. Thereby, each crimping hole 39 opened to the side end crimping plate portion 32 and the stacking end crimping plate portion 33 is fitted into the projection portion 29 of the ducts 6 and 7. Thus, the ducts 6 and 7 are caulked and fixed to the flow path plate 31.

  Next, a state where each part is thermally deformed when the heat exchanger 100 is operated will be described.

  FIG. 6A shows a state before each part of the heat exchanger 100 is thermally deformed. In this state, each part of the tube 9, the support plate 11, and the flow path plate 31 extends linearly along the X-axis direction or the Y-axis direction.

  6B and 7 show a state in which each part of the heat exchanger 100 is thermally deformed. In this state, the support plate 11 and the flow path plate 31 through which the high temperature intake air flows are thermally expanded with respect to the tube 9 through which the low temperature coolant flows. At this time, in particular, the flow path plate 31 having the flow path opening 35 greatly expands by receiving a large amount of intake heat. On the other hand, since the coolant flows through the support plate 11 and each tube 9, the thermal expansion amount of each tube 9 is smaller than that of the flow path plate 31. Thereby, in the frame part 34 of the flow path plate 31, the supported plate part 34 b is pulled in the Y-axis direction (downward in FIG. 6B) by the flow path end plate part 14 of the support plate 11. 34b is thermally deformed to bend in the direction of arrow A about the Z axis.

  The supported plate portion 34b of the flow path plate 31 is urged to bend around the Z axis in the direction of arrow A due to the rigidity being lowered by the flow path plate notch 36. Similarly, the joining plate portion 14a of the support plate 11 is also urged to bend around the Z axis in the direction of arrow A due to the rigidity being lowered by the support plate cutout portion 16. As a result, the stress is dispersed in the flow path plate 31 and the support plate 11, and the stress is prevented from concentrating on the end portion 9a of the tube 9 formed of the thin material.

  In FIG. 6B, a line segment B is a straight line along the supported plate portion 34b and the bonded plate portion 14a that are thermally deformed as described above. The line segment C is a straight line along the supported plate portion 34b and the joining plate portion 14a that are thermally deformed in the comparative example that does not include the flow path plate cutout portion 36 and the support plate cutout portion 16. The line segment B is greatly inclined by the angle θ with respect to the Y axis as compared with the line segment C of the comparative example. As a result, the end 9 a of the tube 9 is restrained from being pulled in the Z-axis direction (upward in FIG. 6B) by the flow path plate 31 and the support plate 11, and thermal distortion that occurs at the joint with the support plate 11 is suppressed. Reduced.

  Next, the effect of this embodiment will be described.

  [1] According to this embodiment, the heat exchanger 100 includes a plurality of tubes 9 through which a coolant flows, a support plate 11 that supports end portions 9a of the tubes 9 to be stacked, and a plurality of tubes 9. And a flow path plate 31 that forms a first flow path 1 (flow path) through which intake air flows. The flow path plate 31 is formed continuously with the supported plate part 34 b joined to the support plate 11, the flow path opening 35 through which the intake air flows through the supported plate part 34 b, and the flow path opening 35. A heat exchanger 100 having a flow path plate cutout 36 that cuts out the supported plate portion 34b is provided.

  With this configuration, the supported plate portion 34b is deformed due to a difference in thermal expansion between the flow path plate 31 and the tube 9 due to a decrease in rigidity due to the flow path plate notch 36. Is prompted. Thereby, the thermal distortion which arises in the edge part 9a of the tube 9 is suppressed small, and durability of the heat exchanger 100 is improved.

  The flow path plate 31 has a sufficient area for joining the support plate 11 in a limited space by the flow path plate notch 36 notching a part of the supported plate portion 34b. Thereby, at the time of manufacture of the heat exchanger 100, the brazing which the flow-path plate 31 and the support plate 11 are joined by a brazing material is performed favorably.

  [2] Further, the support plate 11 has a joining plate portion 14a joined to the supported plate portion 34b, and a support plate cutout portion 16 in which the joining plate portion 14a is cut out so as to coincide with the flow path plate cutout portion 36. .

  With this configuration, the flow path plate 31 and the support plate 11 are less rigid due to the flow path plate notch 36 and the support plate notch 16 that match each other. The deformation is urged by the difference in the amount of thermal expansion occurring between them. Thereby, the thermal distortion which arises in the edge part 9a of the tube 9 is suppressed small.

  [3] The flow path opening 35 has a pair of corners 35 c arranged in the stacking direction (Z-axis direction) of the tubes 9. The flow path plate cutouts 36 are respectively disposed at the pair of corners 35c.

  By configuring in this way, the pair of flow path plate notches 36 arranged at each corner 35c effectively improves the rigidity of the supported plate 34b extending in the stacking direction (Z-axis direction) of the tubes 9. Reduce. Thereby, the thermal distortion which arises in the edge part 9a of the tube 9 is suppressed small.

  As a modification, one flow path plate notch 36 may be disposed between a pair of corners 35c arranged in the stacking direction (Z-axis direction). Compared to this modified example, the pair of flow path plate notches 36 arranged at each corner 35c are separated from each other in the stacking direction (Z-axis direction) of the tube 9, thereby stacking the tube 9 in the stacking direction (Z-axis). The rigidity of the supported plate portion 34b extending in the direction can be effectively reduced.

  [4] The flow path plate notch 36 is formed in the longitudinal direction (Y-axis direction) of the tube 9 from the flow path opening 35.

  With this configuration, the flow path plate notch 36 effectively reduces the rigidity of the supported plate 34b by notching the supported plate 34b in the longitudinal direction (Y-axis direction) of the tube 9. . Thereby, the thermal distortion which arises in the edge part 9a of the tube 9 is suppressed small.

  [5] According to the present embodiment, the heat exchanger 100 includes a plurality of tubes 9 through which a coolant flows and a case 20 that forms a first flow path 1 (flow path) through which intake air flows. . The case 20 includes a pair of support plates 11 that support the end portions 9a of the plurality of tubes 9, and a pair of flow path plates 31 having a rectangular flow path opening 35 through which intake air flows. The flow path plate 31 has a flow path plate notch 36 formed in the longitudinal direction of the tube 9 from the corner 35 c of the flow path opening 35 with the supported plate portion 34 b (both ends) joined to the support plate 11. .

  With this configuration, in the case 20, the pair of flow path plate notches 36 disposed at the respective corners 35 c of the flow path opening 35 are formed on the supported plate portions 34 b (both ends) of the flow path plate 31. Effectively reduce the stiffness. Thereby, the thermal distortion which arises in the edge part 9a of the tube 9 is suppressed small, and durability of the heat exchanger 100 is improved.

  [6] Further, the plate thickness t <b> 2 of the flow path plate 31 is smaller than the plate thickness t <b> 3 of the support plate 11.

  By configuring in this way, the case 20 has sufficient rigidity secured by the flow path plate 31 and the support plate 11, and the thermal strain generated at the end portion 9 a of the tube 9 can be suppressed to be small.

  [7] Further, the flow path plate 31 includes a frame portion 34 on which the ducts 6 and 7 that guide the intake air to the flow path opening 35 are fixed by caulking.

  With this configuration, the case 20 has the flow path plate 31 with increased rigidity by the frame portion 34 to which the ducts 6 and 7 are fixed by caulking, and the outer shape of the flow path plate 31 is maintained.

  The embodiment of the present invention has been described above. However, the above embodiment only shows a part of application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.

  For example, in the above embodiment, the flow path plate 31 is a single member that extends in a frame shape (annular shape) along the flow path opening 35. However, the present invention is not limited to this, and the flow path plate 31 may be a member divided into a plurality along the flow path opening 35.

  Although this invention is suitable as a heat exchanger mounted in a vehicle, it is applicable also to the heat exchanger used other than a vehicle.

9 Tube 9a End 11 Support plate 14a Joint plate 16 Support plate notch 20 Case 31 Channel plate 34 Frame 34b Supported plate 35 Flow channel opening 35c Corner
36 Channel plate notch 100 Heat exchanger

Claims (7)

A heat exchanger in which heat is exchanged between a first fluid and a second fluid,
A plurality of tubes through which the second fluid flows;
A support plate for supporting end portions of the plurality of tubes to be stacked;
A flow path plate that forms a flow path through which the first fluid flows between the tubes,
The flow path plate is
A supported plate portion joined to the support plate;
A flow path opening through which the first fluid flows through the supported plate part;
A heat exchanger having a flow path plate notch formed continuously with the flow path opening and notching the supported plate. The heat exchanger according to claim 1,
The support plate is
A joining plate part joined to the supported plate part;
A heat exchanger comprising: a support plate cutout portion that cuts the joining plate portion so as to match the flow path plate cutout portion. The heat exchanger according to claim 1 or 2,
The flow path opening has a pair of corners arranged in the stacking direction of the tubes,
The heat exchanger according to claim 1, wherein the flow path plate notch is formed at each of the pair of corners. The heat exchanger according to any one of claims 1 to 3,
The flow channel plate notch is formed in the longitudinal direction of the tube from the flow channel opening. A heat exchanger in which heat is exchanged between a first fluid and a second fluid,
A plurality of tubes through which the second fluid flows;
Forming a flow path through which the first fluid flows, and
The case is
A pair of support plates for supporting ends of the plurality of tubes to be stacked;
A pair of flow path plates having rectangular flow path openings through which the first fluid flows,
The flow path plate has flow path plate notches formed in the longitudinal direction of the tube from the corners of the flow path opening, with both ends joined to the support plate.
A heat exchanger characterized by that. A heat exchanger according to any one of claims 1 to 5,
The heat exchanger according to claim 1, wherein a thickness of the flow path plate is smaller than a thickness of the support plate. The heat exchanger according to any one of claims 1 to 6,
The said flow path plate is provided with the frame part by which the duct which guides a 1st fluid to the said flow path opening part is fixed, The heat exchanger characterized by the above-mentioned.

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