Heat Exchanger

Abstract

A heat exchanger includes: first plates; second plates disposed at intervals with each between a pair of the first plates adjacent to each to alternately form first flow paths and second flow paths; and a heat exchange promoting member in the first flow paths. At least one of the first plates and each second plate includes a plurality of protruding portions each of which is formed in a V shape in a plan view such that the protruding portion recesses in a corresponding one of the first flow paths and projects in a corresponding one of the second flow paths. Each protruding portion has a tip end portion and an opening portion arranged in a flow direction in the second flow path, and one of a pair of free end portions is positioned on a first inflow port side and the other is positioned on a first outflow port side.

Description

TECHNICAL FIELD

The present invention relates to a heat exchanger.

BACKGROUND ART

JP2016-090123A discloses a heat exchanger in which a first plate and a second plate are alternately laminated at intervals, a cooling water flow path and an ATF (automatic transmission fluid) flow path are alternately formed, and heat exchange is performed between cooling water and an ATF through the first plate or the second plate. In the heat exchanger, a plurality of ribs that protrude toward the second plate and extend in a flow direction of the cooling water are provided on the first plate, and tip end surfaces of the ribs are in contact with the second plate to block a part of the cooling water flow path between the first plate and the second plate. In addition, in the heat exchanger, an inner fin is provided in the ATF flow path to increase a heat transfer area of the first plate and the second plate.

SUMMARY OF INVENTION

However, in the heat exchanger in JP2016-090123A, since the cooling water flow path is divided by the ribs, the cooling water flows to every corner, but a water stop area is formed on a downstream side of the ribs, water flow resistance of the cooling water is increased, and heat exchange performance may deteriorate. In addition, although the inner fin is provided in the ATF flow path, since the inner fin is not in contact with the first plate at positions where the ribs are provided, the heat exchange performance may deteriorate.

An object of the invention is to improve, in a heat exchanger in which a first plate and a second plate are alternately laminated at intervals and a first fluid flow path and a second fluid flow path are alternately formed, heat exchange performance in both the first fluid flow path and the second fluid flow path.

According to an aspect of the present invention, a heat exchanger configured to perform heat exchange between a first fluid and a second fluid flowing in a direction intersecting the first fluid, the heat exchanger includes: a plurality of first plates provided in parallel at intervals; second plates disposed at intervals with each between a pair of the first plates adjacent to each other, and alternately laminated with the first plates to alternately form first flow paths each allowing the first fluid to flow therethrough and second flow paths each allowing the second fluid to flow therethrough; and a heat exchange promoting member provided in the first flow paths and in contact with the first plates and the second plates, wherein at least one of each of the first plates and each of the second plates includes a plurality of protruding portions each of which is formed in a V shape in a plan view such that the protruding portion recesses in a corresponding one of the first flow paths and projects in a corresponding one of the second flow paths, and each of which is formed to be lower than a flow path height of a corresponding one of the second flow paths, and each of the protruding portions is arranged such that a tip end portion and an opening portion of the V shape are arranged in a flow direction of the second fluid in the second flow path, and one of a pair of free end portions of the V shape is positioned on a first inflow port side on which the first fluid flows toward the first flow paths and the other is positioned on a first outflow port side on which the first fluid flows out from the first flow paths.

In the above aspect, at least one of each of the first plates and each of the second plates includes a plurality of protruding portions each of which is formed in a V shape in a plan view such that the protruding portion recesses in a corresponding one of the first flow paths and projects in a corresponding one of the second flow path and each of whch is formed to be lower than a flow path height of the second flow path. Each of the protruding portions is arranged such that a tip end portion and an opening portion of the V shape are arranged in a flow direction of a second fluid in the second flow path, and one of a pair of free end portions of the V shape is positioned on a first inflow port side on which a first fluid flows toward the first flow path and the other is positioned on a first outflow port side on which the first fluid flows out from the first flow path. Therefore, since the first fluid flows inside the protruding portions and is stirred, the heat exchange performance of the first fluid is improved. In addition, since a longitudinal vortex is generated due to the V-shaped protruding portions in flow of the second fluid, the heat exchange performance of the second fluid is improved. Therefore, the heat exchange performance in both the first fluid flow path and the second fluid flow path can be improved.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a perspective view of a heat exchanger according to an embodiment of the invention when viewed obliquely from above.

FIG. 2 is a perspective view of the heat exchanger when viewed obliquely from below.

FIG. 3 is a longitudinal sectional view of the heat exchanger.

FIG. 4 is a plan view of a first plate.

FIG. 5 is a plan view of a second plate.

FIG. 6 is a plan view showing a state in which the first plate and the second plate are superimposed.

FIG. 7A is a longitudinal sectional view of a round protruding portion.

FIG. 7B is a longitudinal sectional view of a V-shaped protruding portion.

FIG. 8 is a plan view illustrating a relationship between the V-shaped protruding portion and a heat exchange promoting member.

FIG. 9 is a longitudinal sectional view illustrating a relationship between the V-shaped protruding portion and a first flow path.

FIG. 10 is a plan view of a first plate according to a first modification of the heat exchanger according to the embodiment of the invention.

FIG. 11 is a plan view of a second plate.

FIG. 12 is a plan view showing a state in which the first plate and the second plate are superimposed.

FIG. 13 is a plan view of a first plate according to a second modification of the heat exchanger according to the embodiment of the invention.

FIG. 14 is a plan view of a second plate.

FIG. 15A is a longitudinal sectional view of a round protruding portion.

FIG. 15B is a longitudinal sectional view of a V-shaped protruding portion.

FIG. 16 is a plan view of a first plate according to a third modification of the heat exchanger according to the embodiment of the invention.

FIG. 17 is a plan view of a second plate.

FIG. 18 is a plan view illustrating an arrangement of V-shaped protruding portions in a first plate and a second plate according to a fourth modification of the heat exchanger according to the embodiment of the invention.

FIG. 19A is a plan view illustrating a modification of the V-shaped protruding portion.

FIG. 19B is a plan view illustrating another modification of the V-shaped protruding portion.

FIG. 19C is a plan view illustrating still another modification of the V-shaped protruding portion.

FIG. 19D is a plan view illustrating still yet another modification of the V-shaped protruding portion.

DESCRIPTION OF EMBODIMENTS

Hereinafter, a heat exchanger 100 according to an embodiment of the invention will be described with reference to the drawings.

First, an overall configuration of the heat exchanger 100 will be described with reference to FIGS. 1 and 2. FIG. 1 is a perspective view of the heat exchanger 100 according to the embodiment of the invention when viewed obliquely from above, and FIG. 2 is a perspective view of the heat exchanger 100 when viewed obliquely from below.

The heat exchanger 100 is attached to, for example, a vehicle, and uses heat of cooling water of an engine (not illustrated) to warm or cool automatic transmission fluid (ATF).

The heat exchanger 100 includes a core portion 10, a lid member 20, and a bottom plate 30.

As illustrated in FIG. 1, the core portion 10 includes first plates 11, second plates 12, and inner fins 15 (see FIG. 3) serving as a heat exchange promoting member. Heat exchange between the ATF serving as a first fluid and the cooling water serving as a second fluid flowing in a direction intersecting the ATF is performed in the core portion 10. A structure of the core portion 10 will be described later in detail with reference to FIG. 3.

The lid member 20 is attached to an upper surface of the core portion 10. The lid member 20 fixes the core portion 10 from the upper surface. A cooling water inlet 21 through which the cooling water flows into the core portion 10 and a cooling water outlet 22 through which the cooling water flows out from the core portion 10 are connected to the lid member 20. In addition, the lid member 20 includes an ATF return passage 23 formed to protrude upward in order to guide the ATF into the core portion 10.

The bottom plate 30 is attached to a lower surface of the core portion 10. The bottom plate 30 serves as a stand for installing the core portion 10. As illustrated in FIG. 2, a flange 33 including, at four corners, through holes for fixing is formed on the bottom plate 30. The bottom plate 30 includes an ATF inlet 31 through which the ATF flows into the core portion 10 and an ATF outlet 32 through which the ATF flows out from the core portion 10.

Next, the structure of the core portion 10 will be described with reference to FIG. 3 together with FIGS. 1 and 2. FIG. 3 is a longitudinal sectional view of the heat exchanger 100.

As illustrated in FIG. 3, a plurality of first plates 11 are provided in parallel at intervals. The second plate 12 is disposed between a pair of adjacent first plates 11 at intervals. The core portion 10 is constituted by alternately laminating the plurality of first plates 11 and second plates 12 at intervals.

The first plate 11 and the second plate 12 are formed using a flat plate member (plate) made of metal, which transmits heat easily, such that outer peripheries thereof have the same square shape. Corner portions of the first plate 11 and the second plate 12 have a slightly rounded shape to guide flow of the cooling water and the ATF (see FIG. 1).

ATF flow paths 13 serving as a plurality of first flow paths through which the ATF flows and cooling water flow paths 14 serving as a plurality of second flow paths through which the cooling water flows are alternately formed between the adjacent first plate 11 and second plate 12.

The ATF that flows from the ATF inlet 31 of the bottom plate 30 and changes a flow direction at the ATF return passage 23 branches and flows into the plurality of ATF flow paths 13. The ATF that passes through the plurality of ATF flow paths 13 merges and flows out of the heat exchanger 100 from the ATF outlet 32. As illustrated in FIG. 3, the inner fin 15 is provided in each of the ATF flow paths 13.

The cooling water that flows from the cooling water inlet 21 connected to the lid member 20 branches and flows into the plurality of cooling water flow paths 14. The cooling water that passes through the plurality of cooling water flow paths 14 merges and flows out of the heat exchanger 100 from the cooling water outlet 22.

The inner fins 15 are provided in the ATF flow paths 13 and are in contact with the first plates 11 and the second plates 12. The inner fin 15 is a fin for increasing a heat transfer area of the first plate 11 and the second plate 12 and facilitating heat exchange of the ATF flowing through the ATF flow path 13. The ATF flowing through the ATF flow path 13 exchanges heat with the cooling water flowing through the adjacent cooling water flow path 14 via the first plate 11 and the second plate 12.

Cooling water inlet side flow holes 11a are formed at the same position in the plurality of first plates 11 and second plates 12, cooling water outlet side flow holes 11b are formed at the same position in the plurality of first plates 11 and second plates 12, and ATF supply holes 11c are formed at the same positions in the plurality of first plates 11 and second plates 12. By laminating the first plates 11 and the second plates 12, the cooling water inlet side flow hole 11a, the cooling water outlet side flow hole 11b, and the ATF supply hole 11c are arranged so as to penetrate the first plates 11 and the second plates 12 in a lamination direction.

Similarly, although not illustrated, ATF inlet side flow holes 11d are formed at the same position in the plurality of first plates 11 and second plates 12 and ATF outlet side flow holes 11e are formed at the same position in the plurality of first plates 11 and second plates 12. By laminating the first plates 11 and the second plates 12, the ATF inlet side flow hole 11d and the ATF outlet side flow hole 11e are arranged so as to penetrate the first plates 11 and the second plates 12 in the lamination direction.

The cooling water inlet side flow hole 11a is a hole for introducing the cooling water into the cooling water flow path 14 of the core portion 10. The cooling water inlet side flow hole 11a is connected to the cooling water inlet 21 connected to the lid member 20, and allows the cooling water flowing from the cooling water inlet 21 to flow into the cooling water flow path 14. The cooling water flowing into the cooling water flow path 14 flows so as to spread over the entire cooling water flow paths 14.

The cooling water outlet side flow hole 11b is a hole for discharging the cooling water from the cooling water flow path 14. The cooling water outlet side flow hole 11b is connected to the cooling water outlet 22 connected to the lid member 20, and allows the cooling water flowing from the cooling water flow path 14 to flow out to the cooling water outlet 22.

The ATF supply hole 11c is a hole for supplying the ATF into the ATF flow path 13 of the core portion 10 for circulation. By providing the ATF supply hole 11c, an interval between the ATF inlet 31 and the ATF outlet 32 can be reduced. In other words, even when the interval between the ATF inlet 31 and the ATF outlet 32 is small, the heat exchanger 100 can be enlarged.

The ATF flow path 13 and the cooling water flow path 14 are formed as independent flow path systems, and the cooling water and the ATF do not mix with each other. In addition, the cooling water does not leak from the cooling water inlet side flow hole 11a and the cooling water outlet side flow hole 11b to the ATF flow path 13, and the ATF does not leak from the ATF supply hole 11c, the ATF inlet side flow hole 11d, and the ATF outlet side flow hole 11e to the cooling water flow path 14.

Next, the first plate 11 and the second plate 12 will be described with reference to FIGS. 4 to 9. FIG. 4 is a plan view of the first plate 11. FIG. 5 is a plan view of the second plate 12. FIG. 6 is a plan view showing a state in which the first plate 11 and the second plate 12 are superimposed. FIG. 7A is a longitudinal sectional view of a round protruding portion 40. FIG. 7B is a longitudinal sectional view of a V-shaped protruding portion 50. FIG. 8 is a plan view illustrating a relationship between the V-shaped protruding portion 50 and the inner fins 15. FIG. 9 is a longitudinal sectional view illustrating a relationship between the V-shaped protruding portion 50 and the ATF flow path 13.

As illustrated in FIG. 4, the first plate 11 includes the cooling water inlet side flow hole 11a serving as a second inflow port, the cooling water outlet side flow hole 11b serving as a second outflow port, the ATF supply hole 11c, the ATF inlet side flow hole 11d serving as a first inflow port, the ATF outlet side flow hole 11e serving as a first outflow port, the round protruding portions 40, and the V-shaped protruding portions 50 each serving as a protruding portion.

The cooling water inlet side flow hole 11a is formed in a vicinity of a corner portion of one corner of the first plate 11.

The cooling water outlet side flow hole 11b is formed in a vicinity of a corner portion of an opposite corner of the first plate 11 so as to face the cooling water inlet side flow hole 11a with a center of the first plate 11 interposed therebetween. The cooling water outlet side flow hole 11b is formed in the same shape as the cooling water inlet side flow hole 11a. The cooling water outlet side flow hole 11b is disposed point-symmetrically to the cooling water inlet side flow hole 11a with respect to the center of the first plate 11.

The ATF supply hole 11c is formed in the center of the first plate 11. That is, a central axis of the ATF supply hole 11c is the center of the first plate 11.

The ATF inlet side flow hole 11d is formed in a vicinity of a corner portion of a corner different from the opposite corners at which the cooling water inlet side flow hole 11a and the cooling water outlet side flow hole 11b are provided.

The ATF outlet side flow hole 11e is formed in a vicinity of a corner portion of an opposite corner of the first plate 11 so as to face the ATF inlet side flow hole 11d with the center of the first plate 11 interposed therebetween. The ATF outlet side flow hole 11e is formed in the same shape as the ATF inlet side flow hole 11d. The ATF outlet side flow hole 11e is disposed point-symmetrically to the ATF inlet side flow hole 11d with respect to the center of the first plate 11.

In this way, the cooling water inlet side flow hole 11a, the cooling water outlet side flow hole 11b, the ATF inlet side flow hole 11d, and the ATF outlet side flow hole 11e are provided at the four corners of the first plate 11. Accordingly, the cooling water flowing from the cooling water inlet side flow hole 11a toward the cooling water outlet side flow hole 11b and the ATF flowing from the ATF inlet side flow hole 11d toward the ATF outlet side flow hole 11e flow in directions intersecting each other in the heat exchanger 100.

The round protruding portion 40 is at the same position as the round protruding portion 40 of the second plate 12 in a state in which the first plate 11 and the second plate 12 are laminated. As illustrated in FIG. 7A, the round protruding portion 40 and the round protruding portion 40 of the second plate 12 have the same height as a flow path height of the cooling water flow path 14. Accordingly, in a state in which the first plate 11 and the second plate 12 are laminated, the round protruding portion 40 is abutted with the round protruding portion 40 of the second plate 12 and has a columnar shape. The round protruding portion 40 has a function of maintaining the flow path height of the cooling water flow path 14 when the first plate 11 and the second plate 12 are laminated and assembled.

As illustrated in FIG. 4, a plurality of the round protruding portions 40 are provided in an entire area of the first plate 11. In particular, the round protruding portions 40 are arranged around the cooling water inlet side flow hole 11a, the cooling water outlet side flow hole 11b, the ATF supply hole 11c, the ATF inlet side flow hole 11d, and the ATF outlet side flow hole 11e. In addition, the round protruding portions 40 are arranged so as to interpose the V-shaped protruding portion 50 in a pair. Accordingly, when the first plate 11 and the second plate 12 are laminated and assembled, the flow path height of the cooling water flow path 14 at a position where dimension management is required can be maintained at a specified height. In addition, by providing the round protruding portion 40, the inner fins 15 can be brought into close contact with the first plate 11 and the second plate 12 during brazing.

As illustrated in FIG. 7B, the V-shaped protruding portion 50 is formed in a V shape in a plan view such that the V-shaped protruding portion 50 recesses in the ATF flow path 13 and projects in the cooling water flow path 14. The V-shaped protruding portion 50 is formed to be lower than the flow path height of the cooling water flow path 14. That is, since the V-shaped protruding portion 50 is not in contact with the second plate 12, the V-shaped protruding portion 50 does not block the cooling water flow path 14. Accordingly, an increase in flow path resistance in the cooling water flow path 14 can be suppressed.

As illustrated in FIG. 4, the V-shaped protruding portion 50 is disposed such that a tip end portion 51 and an opening portion 52 of the V shape are arranged in a flow direction of the cooling water in the cooling water flow path 14, and one of a pair of free end portions 53 and 54 of the V shape is positioned on an ATF inlet side flow hole 11d side and the other is positioned on an ATF outlet side flow hole 11e side.

A longitudinal vortex is generated in the cooling water flowing in the cooling water flow path 14 when the cooling water passes over the V-shaped protruding portion 50 having a V-shape. Accordingly, the cooling water flowing in the cooling water flow path 14 is stirred, so that heat exchange performance of the cooling water is improved.

A plurality of V-shaped protruding portions 50 are arranged side by side in an orthogonal direction orthogonal to the flow of the cooling water, and a pair of adjacent V-shaped protruding portions 50 are arranged such that the tip end portion 51 and opening portion 52 of the V shape are alternately arranged in the orthogonal direction.

Accordingly, since the tip end portion 51 and opening portion 52 of the V shape are arranged alternately, that is, the adjacent V-shaped protruding portions 50 are arranged with different orientations, an interval between the adjacent V-shaped protruding portions 50 can be reduced.

A function of stirring the cooling water is the same between a case where the tip end portion 51 is positioned on an upstream side and the opening portion 52 is positioned on a downstream side in the flow direction of the cooling water in the cooling water flow path 14, and a case where the opening portion 52 is positioned on the upstream side and the tip end portion 51 is positioned on the downstream side in the flow direction of the cooling water. This is because, in either case, a straight line portion from the tip end portion 51 toward the free end portion 53 and a straight line portion from the tip end portion 51 toward the free end portion 54 are formed obliquely with respect to the flow direction of the cooling water.

The V-shaped protruding portions 50 on one side of a straight line (straight line O in FIG. 6) connecting the cooling water inlet side flow hole 11a and the cooling water outlet side flow hole 11b are point-symmetrical to the V-shaped protruding portions 50 on the other side of the straight line (straight line O in FIG. 6) with respect to the center of the first plate 11.

Therefore, since the V-shaped protruding portions 50 on the one side and the other side of the straight line connecting the cooling water inlet side flow hole 11a and the cooling water outlet side flow hole 11b are point-symmetrically arranged, and are arranged in the same manner even when being rotated by 180 degrees. Therefore, the first plate 11 and the second plate 12 can be easily assembled.

As illustrated in FIG. 5, the second plate 12 also includes the cooling water inlet side flow hole 11a serving as the second inflow port, the cooling water outlet side flow hole 11b serving as the second outflow port, the ATF supply hole 11c, the ATF inlet side flow hole 11d serving as the first inflow port, the ATF outlet side flow hole 11e serving as the first outflow port, the round protruding portions 40, and the V-shaped protruding portions 50 each serving as the protruding portion.

The cooling water inlet side flow hole 11a, the cooling water outlet side flow hole 11b, the ATF supply hole 11c, the ATF inlet side flow hole 11d, the ATF outlet side flow hole 11e, and the round protruding portion 40 are the same as in the first plate 11, and thus the description thereof is omitted here.

In a vicinity of the cooling water inlet side flow hole 11a, the V-shaped protruding portions 50 are provided radially from the cooling water inlet side flow hole 11a so as to make flow of the flowing cooling water spread over an entire area of the cooling water flow path 14. Similarly, in a vicinity of the cooling water outlet side flow hole 11b, the V-shaped protruding portions 50 are provided radially from the cooling water outlet side flow hole 11b so as to collect flow of the flowing cooling water from the entire area of the cooling water flow path 14.

At a position away from the cooling water inlet side flow hole 11a and the cooling water outlet side flow hole 11b, the V-shaped protruding portion 50 is disposed such that the tip end portion 51 and the opening portion 52 of the V shape are arranged in the flow direction of the cooling water in the cooling water flow path 14, and one of the pair of free end portions 53 and 54 of the V shape is positioned on the ATF inlet side flow hole 11d side and the other is positioned on the ATF outlet side flow hole 11e side.

Similarly, in the second plate 12, the V-shaped protruding portions 50 on one side of the straight line (straight line O in FIG. 6) connecting the cooling water inlet side flow hole 11a and the cooling water outlet side flow hole 11b are also point-symmetrical to the V-shaped protruding portions 50 on the other side of the straight line (straight line O in FIG. 6) with respect to a center of the second plate 12.

As illustrated in FIG. 6, in the heat exchanger 100, the V-shaped protruding portion 50 of the first plate 11 and the V-shaped protruding portion 50 of the second plate 12 are alternately provided in the flow direction of the cooling water flow path 14.

As illustrated in FIG. 8, the inner fin 15 has a heat exchange wall surface 15a erected between the first plate 11 and the second plate 12, and the heat exchange wall surface 15a is disposed to intersect the flow direction of ATF from the ATF inlet side flow hole 11d to the ATF outlet side flow hole 11e.

As illustrated in FIG. 9, since the V-shaped protruding portion 50 is formed to recess in the ATF flow path 13, the ATF flows inside the V-shaped protruding portion 50 at a position where the V-shaped protruding portion 50 is provided. In this way, since the ATF flows inside the V-shaped protruding portion 50 and is stirred, heat exchange performance of the ATF is improved. In addition, the ATF flows inside the V-shaped protruding portion 50, and thus flow path resistance in the ATF flow path 13 can be reduced.

In this way, the first plate 11 and the second plate 12 include the plurality of V-shaped protruding portions 50 each formed in a V shape in a plan view such that the V-shaped protruding portion 50 recesses in the ATF flow path 13 and projects in the cooling water flow path 14 and formed to be lower than the flow path height of the cooling water flow path 14. The V-shaped protruding portion 50 is disposed such that the tip end portion 51 and the opening portion 52 of the V shape are arranged in the flow direction of the cooling water in the cooling water flow path 14, and one of the pair of free end portions 53 and 54 of the V shape is positioned on the ATF inlet side flow hole 11d side and the other is positioned on the ATF outlet side flow hole 11e side. Therefore, since the ATF flows inside the V-shaped protruding portion 50 and is stirred, the heat exchange performance of the ATF is improved. In addition, since the longitudinal vortex is generated due to the V-shaped protruding portion 50 having a V shape in the flow of the cooling water, the heat exchange performance of the cooling water is improved. Therefore, the heat exchange performance of both the ATF flow path 13 and the cooling water flow path 14 can be improved.

In the present embodiment, the V-shaped protruding portion 50 is provided on both the first plate 11 and the second plate 12. However, the V-shaped protruding portion 50 may be provided on at least one of the first plate 11 and the second plate 12.

Next, a first modification of the heat exchanger 100 according to the embodiment of the invention will be described with reference to FIGS. 10 to 12. FIG. 10 is a plan view of the first plate 11 according to the first modification of the heat exchanger 100. FIG. 11 is a plan view of the second plate 12. FIG. 12 is a plan view showing a state in which the first plate 11 and the second plate 12 are superimposed. In each modification shown below, differences from the above-described embodiment are mainly described, and configurations having similar functions are denoted by the same reference numerals and the description thereof is omitted.

The first modification is different from the above-described embodiment in that the ATF supply hole 11c is not provided. In this case, the ATF inlet 31 communicates with the ATF inlet side flow hole 11d. An ATF flowing from the ATF inlet 31 of the bottom plate 30 branches and flows into the ATF flow paths 13. The ATF that passes through the plurality of ATF flow paths 13 merges and flows out of the heat exchanger 100 from the ATF outlet 32.

In the first modification, since the ATF supply holes 11c are not provided at centers of the first plate 11 and the second plate 12, the V-shaped protruding portions 50 can be provided at the position. Accordingly, a water stop area can be reduced, and a longitudinal vortex is generated in cooling water due to the V-shaped protruding portion 50 and the ATF is stirred, heat exchange performance of both the ATF flow path 13 and the cooling water flow path 14 can be improved.

Next, a second modification of the heat exchanger 100 according to the embodiment of the invention will be described with reference to FIGS. 13 to 15B. FIG. 13 is a plan view of the first plate 11 according to the second modification of the heat exchanger 100. FIG. 14 is a plan view of the second plate 12. FIG. 15A is a longitudinal sectional view of the round protruding portion 40. FIG. 15B is a longitudinal sectional view of the V-shaped protruding portion 50.

In the second modification, the adjacent V-shaped protruding portions 50 are connected such that the adjacent V-shaped free end portions 53 and 54 are continuous.

Accordingly, since the free end portions 53 and 54 of the V-shaped protruding portion 50 are formed to be continuous, a contact area where an ATF having a higher viscosity than cooling water comes into contact with the first plate 11 and the second plate 12 increases. Therefore, heat exchange of the ATF flowing through the ATF flow path 13 can be promoted.

In the second modification, the V-shaped protruding portion 50 of the first plate 11 and the V-shaped protruding portion 50 of the second plate 12 are provided such that the tip end portion 51 and the opening portion 52 are arranged with different orientations at the same position. That is, the V-shaped protruding portion 50 of the first plate 11 and the V-shaped protruding portion 50 of the second plate 12 are formed so as to intersect at two points in a plan view.

As illustrated in FIG. 15A, in a state in which the first plate 11 and the second plate 12 are laminated, the round protruding portion 40 of the first plate 11 and the round protruding portion 40 of the second plate 12 are in contact with each other and have a columnar shape. On the other hand, as illustrated in FIG. 15B, at the two points at which the V-shaped protruding portion 50 of the first plate 11 and the V-shaped protruding portion 50 of the second plate 12 intersect, the opposing V-shaped protruding portions 50 are not in contact with each other. That is, the cooling water flow path 14 is also formed between the opposing V-shaped protruding portions 50. Accordingly, heat exchange performance can be improved while suppressing an increase in flow path resistance in the cooling water flow path 14.

Next, a third modification of the heat exchanger 100 according to the embodiment of the invention will be described with reference to FIGS. 16 and 17. FIG. 16 is a plan view of the first plate 11 according to the third modification of the heat exchanger 100. FIG. 17 is a plan view of the second plate 12.

In the third modification, the adjacent V-shaped protruding portions 50 are also connected such that the adjacent V-shaped free end portions 53 and 54 are continuous.

Accordingly, since the free end portions 53 and 54 of the V-shaped protruding portion 50 are formed to be continuous, a contact area where an ATF having a higher viscosity than cooling water comes into contact with the first plate 11 and the second plate 12 increases. Therefore, heat exchange of the ATF flowing through the ATF flow path 13 can be promoted.

In the third modification, the V-shaped protruding portions 50 are provided not only in a vicinity of the cooling water inlet side flow hole 11a but also in an entire area radially from the cooling water inlet side flow hole 11a and the cooling water outlet side flow hole 11b. Accordingly, flow of the flowing cooling water can be expanded over the entire area of the cooling water flow path 14, and flow of the flowing cooling water can be collected from the entire area of the cooling water flow path 14.

In the third modification, the V-shaped protruding portion 50 of the first plate 11 and the V-shaped protruding portion 50 of the second plate 12 are also provided such that the tip end portion 51 and the opening porti52 are arranged with different orientations at the same position. That is, the V-shaped protruding portion 50 of the first plate 11 and the V-shaped protruding portion 50 of the second plate 12 are formed so as to intersect at two points in a plan view.

The round protruding portion 40 is provided at each of the intersecting points. Accordingly, by providing the round protruding portion 40 at a position where a flow path area of the cooling water flow path 14 is small, a water stop area can be reduced as compared with a case where the round protruding portion 40 is provided independently of the V-shaped protruding portion 50.

In the third modification, arc-shaped protruding portions 60 each having an arc shape are provided between the cooling water inlet side flow hole 11a and an outer periphery end portion of the first plate 11, between the cooling water outlet side flow hole 11b and an outer periphery end portion of the first plate 11, between the ATF inlet side flow hole 11d and an outer periphery end portion of the first plate 11, and between the ATF outlet side flow hole 11e and an outer periphery end portion of the first plate 11. The same applies to the second plate 12. Accordingly, the cooling water flowing between the cooling water inlet side flow hole 11a and the outer periphery end portion of the first plate 11, between the cooling water outlet side flow hole 11b and the outer periphery end portion of the first plate 11, between the ATF inlet side flow hole 11d and the outer periphery end portion of the first plate 11, and between the ATF outlet side flow hole 11e and the outer periphery end portion of the first plate 11 can be rectified.

Next, a fourth modification of the heat exchanger 100 according to the embodiment of the invention will be described with reference to FIG. 18. FIG. 18 is a plan view illustrating an arrangement of the V-shaped protruding portions 50 in the first plate 11 and the second plate 12 according to the fourth modification of the heat exchanger 100.

In the fourth modification, the V-shaped protruding portions 50 are alternately arranged on the first plate 11 and the second plate 12 in a direction of a straight line connecting the ATF inlet side flow hole 11d and the ATF outlet side flow hole 11e.

Similarly, in the fourth modification, since a longitudinal vortex is generated in cooling water due to the V-shaped protruding portion 50 and the ATF is stirred, heat exchange performance of both the ATF flow path 13 and the cooling water flow path 14 can be improved.

According to the above embodiment, the following effects are achieved.

The heat exchanger 100 that performs heat exchange between the ATF and the cooling water flowing in the direction intersecting the ATF includes: the plurality of first plates 11 provided in parallel at intervals; the second plates 12 disposed at intervals with each between a pair of the first plates 11 adjacent to each other, and alternately laminated with the first plates 11 to alternately form the ATF flow paths 13 each allowing the ATF to flow therethrough and the cooling water flow paths 14 each allowing the cooling water to flow therethrough; and the inner fins 15 provided in the ATF flow paths 13 and in contact with the first plates 11 and the second plates 12. At least one of each of the first plates 11 and each of the second plates 12 includes the plurality of V-shaped protruding portions 50 each of which is formed in a V shape in a plan view such that the V-shaped protruding portion 50 recesses in a corresponding one of the ATF flow paths 13 and projects in a corresponding one of the cooling water flow paths 14, and each of which is formed to be lower than the flow path height of a corresponding one of the cooling water flow paths 14, and each of the V-shaped protruding portions 50 is arranged such that the tip end portion 51 and the opening portion 52 of the V shape are arranged in the flow direction of the cooling water in the cooling water flow path 14, and the one of the pair of free end portions 53 and 54 of the V shape is positioned on the ATF inlet side flow hole 11d side and the other is positioned on the ATF outlet side flow hole 11e side.

In the configuration, at least one of each of the first plates 11 and each of the second plates 12 includes the plurality of V-shaped protruding portions 50 each of which is formed in a V shape in a plan view such that the V-shaped protruding portion 50 recesses in the ATF flow path 13 and projects in the cooling water flow path 14 and each of which is formed to be lower than the flow path height of the cooling water flow path 14. Each of the V-shaped protruding portions 50 is arranged such that the tip end portion 51 and opening portion 52 of the V shape are arranged in the flow direction of the cooling water in the cooling water flow path 14, and one of the pair of free end portions 53 and 54 of the V shape is positioned on the ATF inlet side flow hole 11d side and the other is positioned on the ATF outlet side flow hole 11e side. Therefore, since the ATF flows inside the V-shaped protruding portion 50 and is stirred, the heat exchange performance of the ATF is improved. In addition, since the longitudinal vortex is generated due to the V-shaped protruding portion 50 having a V shape in the flow of the cooling water, the heat exchange performance of the cooling water is improved. Therefore, the heat exchange performance of both the ATF flow path 13 and the cooling water flow path 14 can be improved.

Although the embodiment of the present invention has been described in the above, the above-mentioned embodiment merely illustrates a part of application examples of the present invention, and the technical scope of the present invention is not intended to be limited to the specific configurations of the above-described embodiment.

For example, the V-shaped protruding portion 50 may have shapes as illustrated in FIGS. 19A to 19D. FIGS. 19A to 19D are plan views illustrating modifications of the V-shaped protruding portion 50.

In the modification of the V-shaped protruding portion 50 illustrated in FIG. 19A, the tip end portion 51 is formed in an arc shape. In the modification of the V-shaped protruding portion 50 illustrated in FIG. 19B, not only the tip end portion 51 but also the entire space between the free end portions 53 and 54 are formed in an arc shape and have a substantially U shape. In the modification of the V-shaped protruding portion 50 illustrated in FIG. 19C, a straight line portion is further provided toward the free end portions 53 and 54 with respect to the modification illustrated in FIG. 19B, and a substantially U shape is made. In the modification of the V-shaped protruding portion 50 illustrated in FIG. 19D, the tip end portion 51 is divided into two and has a substantially W shape. The modifications illustrated in FIGS. 19A to 19D are also included in the V-shaped protruding portion 50 formed in a V shape.

In the above embodiment, the first fluid is the ATF and the second fluid is the cooling water. However, the first fluid and the second fluid are not limited thereto.

The present application claims a priority based on Japanese Patent Application No. 2021-062949 filed with the Japan Patent Office on Apr. 1, 2021, the entire content of which are incorporated into this specification by reference.

Claims

1. A heat exchanger configured to perform heat exchange between a first fluid and a second fluid flowing in a direction intersecting the first fluid, the heat exchanger comprising:

a plurality of first plates provided in parallel at intervals;

second plates disposed at intervals with each between a pair of the first plates adjacent to each other, and alternately laminated with the first plates to alternately form first flow paths each allowing the first fluid to flow therethrough and second flow paths each allowing the second fluid to flow therethrough; and

a heat exchange promoting member provided in the first flow paths and in contact with the first plates and the second plates, wherein

at least one of each of the first plates and each of the second plates includes a plurality of protruding portions each of which is formed in a V shape in a plan view such that the protruding portion recesses in a corresponding one of the first flow paths and projects in a corresponding one of the second flow paths, and each of which is formed to be lower than a flow path height of a corresponding one of the second flow paths,

the plurality of protruding portions are arranged side by side in an orthogonal direction orthogonal to flow of the second fluid such that a tip end portion and an opening portion of the V shape are arranged in a flow direction of the second fluid in the second flow paths, and one of a pair of free end portions of the V shape is positioned on a first inflow port side on which the first fluid flows toward the first flow paths and the other is positioned on a first outflow port side on which the first fluid flows out from the first flow paths,

the protruding portion on one side of a straight line connecting a second inflow port allowing the second fluid to flow into the second flow paths and a second outflow port allowing the second fluid to flow out from the second flow paths is point-symmetrical to the protruding portion on the other side of the straight line with respect to centers of the first plates and the second plates, and

a pair of the protruding portions adjacent to each other are arranged such that the tip end portion and the opening portion of the V shape are alternately arranged in the orthogonal direction.

2. The heat exchanger according to claim 1, wherein

the heat exchange promoting member has a heat exchange wall surface erected between the first plate and the second plate, and

the heat exchange wall surface is disposed so as to intersect a flow direction of the first fluid from a first inflow port toward a first outflow port.

3. (canceled)

4. (canceled)

5. (canceled)

6. (canceled)