CN118541580A - Heat exchanger - Google Patents

Abstract

An oil cooler (2) as a heat exchanger is provided with a male plate (100), wherein the male plate (100) has an upper surface (100 a), and a plurality of protrusions (104) extending linearly are formed on the upper surface (100 a) as a first surface on which cooling water, which is a heat supply medium, contacts.

Description

Heat exchanger

Technical Field

The present invention relates to a heat exchanger.

Background

There is a heat exchanger in which a plurality of plate members are stacked, alternately formed in a stacking direction of the plate members: a flow path through which a gas or oil flows, and a flow path through which cooling water flows (patent document 1).

Prior art literature

Patent literature

Patent document 1: japanese patent No. 4527557

Disclosure of Invention

First, the technical problem to be solved

The heat exchanger of patent document 1 is provided with embossing or protruding bodies in the first flow path, and a heat exchanger having high heat exchange performance is desired.

The present invention has been made in view of the above circumstances, and an object thereof is to provide a heat exchanger having high heat exchange performance.

(II) technical scheme

In order to solve the above-described problems, a heat exchanger is provided that includes a first plate having a first surface that is in contact with a heating medium, and a plurality of first protrusions extending in a linear shape are formed on the first surface.

(III) beneficial effects

According to the heat exchanger of the invention, the heat exchange performance is improved.

Drawings

Fig. 1 is a schematic diagram showing a heat exchange system 1.

Fig. 2 is a perspective view of the oil cooler 2.

Fig. 3 is an exploded view of the oil cooler 2.

Fig. 4 is an exploded view of the plate assembly 60.

Fig. 5 is an exploded view of the overlapping joint of two plate assemblies 60.

Fig. 6 is a top view of male plate 100.

Fig. 7 is a bottom view of the male plate 100.

Fig. 8 is a top view of the female plate 110.

Fig. 9 is a bottom view of the female plate 110.

Fig. 10 is a top view of the plate assembly 60.

Fig. 11 is a cross-sectional view of the plate assembly 60.

Fig. 12 is a schematic diagram showing the flow of cooling water.

Fig. 13 is a schematic view showing the flow of oil.

Fig. 14 is a perspective view of an oil cooler 2 according to modification 18.

Detailed Description

Embodiments of the present invention will be described below with reference to the drawings. However, although various limitations technically preferable for carrying out the present invention are attached to the embodiments described below, the scope of the present invention is not limited to the following embodiments and examples.

(Outline of Heat exchange System)

Fig. 1 is a schematic diagram of a heat exchange system 1. The heat exchange system 1 includes: an oil cooler 2, an engine 3, an oil pump 4, a radiator 5, a water pump 6, an oil flow path 7, and a cooling water flow path 8.

The oil cooler 2 is a heat exchanger. The oil cooler 2 exchanges heat between high-temperature engine oil discharged from the engine 3 and low-temperature cooling water cooled by the radiator 5.

The oil flow path 7 is a flow path through which engine oil flows. The oil flow path 7 is connected by piping between the engine 3 and the oil cooler 2, between the oil cooler 2 and the oil pump 4, and between the oil pump 4 and the engine 3, respectively, and circulates engine oil in the arrow direction in fig. 1.

The engine oil at a high temperature discharged from the engine 3 is supplied to the oil cooler 2. The engine oil is cooled by the oil cooler 2 and supplied to the oil pump 4. Engine oil is supplied to the engine 3 by an oil pump 4.

The cooling water flow path 8 is a flow path through which cooling water flows. The cooling water flow path 8 is connected by piping between the radiator 5 and the water pump 6, between the water pump 6 and the oil cooler 2, and between the oil cooler 2 and the radiator 5, respectively, and circulates cooling water in the direction of the arrow in fig. 1.

The cooling water discharged from the radiator 5 is supplied to the oil cooler 2 by a water pump 6. The cooling water cools the engine oil in the oil cooler 2 to a high temperature. The cooling water having a high temperature is supplied from the oil cooler 2 to the radiator 5. The cooling water is cooled by the radiator 5.

(Structure of oil cooler)

Fig. 2 (a) is a perspective view of the oil cooler 2. The oil cooler 2 includes: a bottom flange 10, and a heat exchange portion 20.

(Bottom flange)

The bottom flange 10 is a member for attaching the oil cooler 2 to another structure such as an engine block. The bottom flange 10 is a metal plate. The bottom flange 10 has: a plurality of through holes 11, oil inflow and outflow ports 12a and 12b, and cooling water inflow and outflow ports 13a and 13b. Fig. 3 is an exploded view of the oil cooler 2.

Here, the up-down direction is defined as: in a direction parallel to the thickness of the bottom flange 10. As shown in fig. 3, a direction orthogonal to the vertical direction is defined as a front-rear direction, and a direction orthogonal to the vertical direction and the front-rear direction is defined as a left-right direction.

The through hole 11 is a hole for screw fixation. The through hole 11 is a hole penetrating the bottom flange 10 in the up-down direction. The through hole 11 is provided at the outer peripheral edge of the bottom flange 10 so as not to overlap with the mounting portion of the heat exchange portion 20. In the present embodiment, six through holes 11 are provided in the bottom flange 10. By fitting a bolt, not shown, into the through hole 11, the bolt is fastened to another structure, and the oil cooler 2 is attached to the other structure.

The oil inflow and outflow ports 12a, 12b are openings through which engine oil flows. In the present embodiment, the rear opening of the bottom flange 10 is used as the oil inflow port 12a, and the front opening is used as the oil outflow port 12 b.

The cooling water inflow outlets 13a, 13b are openings through which cooling water flows. In the present embodiment, the rear opening of the bottom flange 10 is used as the cooling water inlet 13a, and the front opening is used as the cooling water outlet 13 b. The cooling water inlet 13a has: small diameter opening 14a, large diameter opening 15a. The small diameter opening 14a is provided from the lower surface of the bottom flange 10 toward the upper surface side, and is connected to the large diameter opening 15a. A large-diameter opening 15a is provided upward from the small-diameter opening 14a to the upper surface of the bottom flange 10. The large-diameter opening 15a is larger than the small-diameter opening 14a in plan view, and the small-diameter opening 14a is disposed inside the large-diameter opening 15a. The cooling water outflow port 13b has: small diameter opening 14b, large diameter opening 15b. The structures of the small diameter opening 14b and the large diameter opening 15b are the same as those of the small diameter opening 14a and the large diameter opening 15a.

(Heat exchange portion)

The heat exchange portion 20 is a structure in which flow paths for engine oil and cooling water are formed as fluid, respectively, and heat exchange is performed between the two fluids flowing along the respective flow paths. The heat exchange unit 20 includes: a bottom plate 30, a lamination portion 40, and a top plate 50. The heat exchange portion 20 includes a lamination portion 40 laminated on an upper surface of the bottom plate 30, and a top plate 50 laminated on an upper surface of the lamination portion 40.

(Baseboard)

The bottom plate 30 is a member disposed at the lowest layer of the heat exchange portion 20 and attached to the bottom flange 10. The bottom plate 30 is attached to the lower surface of the lowermost plate of the laminated portion 40. In the present embodiment, the bottom plate 30 is a male plate 100 described later.

(Laminate section)

The lamination portion 40 is a structure that laminates the plate members in the up-down direction and forms flow paths for engine oil and cooling water, respectively. The lamination portion 40 is laminated with a plurality of board assemblies 60 and joined by welding. In the present embodiment, the lamination portion 40 is laminated with four board assemblies 60.

(Board Assembly)

The plate assembly 60 has: a male plate 100, a female plate 110, and fins 120. Fig. 4 is an exploded view of the plate assembly 60. The plate assembly 60 is stacked with the male plate 100 as an upper side and the female plate 110 as a lower side, with the fins 120 disposed therebetween. A space is formed between the male plate 100 and the female plate 110 in the plate assembly 60, and functions as a second flow path 132 through which engine oil flows.

Fig. 5 is a diagram of an arrangement in which the female plate 110 is the upper side and the male plate 100 is the lower side. When two plate assemblies 60 are stacked, a female plate 110 and a male plate 100 are arranged at the joint portions thereof as shown in fig. 5. A space is formed between the female plate 110 and the male plate 100 at the joint portion of the two plate assemblies 60, and functions as a first flow passage 131 through which cooling water flows.

(Structure of flow passage of oil cooler)

Fig. 2 (b) is a simplified diagram of the section of the IIb position of fig. 2 (a). The bottom plate 30 is provided on the upper surface of the bottom flange 10. The female plate 110 and the male plate 100 are alternately disposed in the up-down direction on the bottom plate 30.

The space formed by providing the female plate 110 on the male plate 100 is the first flow path 131. The space formed by providing the male plate 100 on the female plate 110 is the second flow path 132. The first flow path 131 and the second flow path 132 are alternately formed in the up-down direction. The first flow path 131 and the second flow path 132 are separated by the male plate 100 and the female plate 110, and thus are independent of each other.

The cooling water flows in from the cooling water inlet 13a and flows into the first flow path 131. After flowing through the first flow path 131, the cooling water reaches the cooling water outflow port 13b. The cooling water flows out from the cooling water outflow port 13b to the radiator 5.

The engine oil flows in from the oil inflow port 12a and flows into the second flow path 132. After flowing through the second flow path 132, the engine oil reaches the oil outlet 12b. The engine oil flows out from the oil outflow port 12b to the oil pump 4.

(Male plate)

The male plate 100 is a member for performing heat exchange between two fluids (engine oil and cooling water) flowing along the upper and lower surfaces. The male plate 100 is a metal plate material smaller than the bottom flange 10 by one turn. Fig. 6 is a top view of male plate 100. The male plate 100 is formed in a substantially rectangular shape having a long side extending in the front-rear direction and a short side extending in the left-right direction in a plan view. The male plate 100 has: an upper surface 100a formed with linear protrusions 104, a lower surface 100b formed with linear grooves 105, edges 106 formed with oil inflow and outflow ports 102a, 102b, and edges 107 formed with cooling water inflow and outflow ports 103a, 103 b.

The oil inflow and outflow ports 102a, 102b are openings through which engine oil flows. The oil inflow and outflow ports 102a, 102b are provided at a set of diagonal positions among the four corners of the male plate 100. The opening size of the oil inflow and outflow openings 102a, 102b is larger than the oil inflow and outflow openings 12a, 12b of the bottom flange 10. In the present embodiment, the opening at the rear right of the male plate 100 in fig. 6 is used as the oil inflow port 102a, and the opening at the front left of the male plate 100 is used as the oil outflow port 102 b. The rim portions 106 of the oil inflow and outflow ports 102a, 102b protrude upward and the upper surfaces thereof are flat.

The cooling water inflow outlets 103a, 13b are openings through which cooling water flows. The cooling water inflow outlets 103a, 103b are provided at a set of diagonal positions of the four corners of the male plate 100 where the oil inflow outlets 102a, 102b are not provided. In the present embodiment, the left rear opening of the male plate 100 of fig. 6 is used as the cooling water inflow port 103a, and the right front opening is used as the cooling water outflow port 103 b. The opening sizes of the cooling water inflow outlets 103a, 103b are the same as those of the large diameter openings 15a, 15 b. The rim 107 protrudes downward and its lower surface is planar. The shape of the edge 107 corresponds to the shape of the large diameter openings 15a, 15 b. The length of the downward projection of the edge 107 corresponds to the depth of the large diameter openings 15a, 15 b.

The protrusions 104 are protrusions that cause the fluid flowing along the upper surface 100a to flow irregularly, protrude upward from the flat portion of the upper surface 100a, and extend straight in a plan view. The protrusions 104 are provided in plurality on the upper surface 100 a. The upper surface 100a is divided into two regions 108a, 108b, and a plurality of protrusions 104 are provided in each region 108a, 108b.

The areas 108a and 108b are areas defined on the upper surface 100 a. The regions 108a, 108b are rectangular extending in the front-rear direction. The areas 108a, 108b are substantially symmetrically divided on the left and right of the upper surface 100 a. In the present embodiment, the region provided on the left side of the upper surface 100a is a region 108a, and the region provided on the right side is a region 108b.

Here, for the sake of explanation, the protrusions 104 provided in the respective regions 108a and 108b are set as protrusions 104a and 104b, respectively. The plurality of projections 104a provided in the region 108a are provided in parallel with each other, and the plurality of projections 104b provided in the region 108b are also provided in parallel with each other. In addition, the protrusion 104a extends in a direction intersecting the protrusion 104b. The plurality of protrusions 104a and 104b form a so-called herringbone pattern in a plan view.

As shown in fig. 11, the height of the protrusion 104 is about one half of the height of the space (first flow path 131) formed when the female plate 110 is overlapped on the male plate 100. The protrusion 104 has a joint 101 of dot-like protrusions. The joint 101 is provided at a position where the protrusion 104 intersects the protrusion 114 when the female plate 110 is superimposed on the male plate 100 in a plan view.

The grooves 105 are grooves that make the flow of the fluid flowing along the lower surface 100b irregular. Fig. 7 is a bottom view of the male plate 100. The plurality of grooves 105 are provided so as to be recessed upward from the flat portion of the lower surface 100b, and extend linearly in a plan view. Since the grooves 105 and the protrusions 104 are formed by press working, the grooves 105 have the same shape as the protrusions 104 in the vertical direction. The groove 105 overlaps the protrusion 104 in plan view. That is, each groove 105 is provided on the lower surface 100b in a pair with the projection 104 having the same shape. The lower surface 100b is divided into two areas 108c and 108d, and a plurality of grooves 105 are provided in each of the areas 108c and 108d.

The areas 108c and 108d are areas defined on the lower surface 100 b. The regions 108c, 108d are rectangles extending in the front-rear direction. The areas 108c and 108d are substantially symmetrically divided on the lower surface 100 b. In the present embodiment, the region provided on the right side of the lower surface 100b is a region 108c, and the region provided on the left side is a region 108d. The region provided on the back surface of the region 108a is a region 108c, and the region provided on the back surface of the region 108b is a region 108d.

Here, the grooves 105 provided in the respective regions 108c and 108d are set as grooves 105a and 105b, respectively, for the sake of explanation. The grooves 105a and 105b are paired with the protrusions 104a and 104b having the same shape. The plurality of grooves 105a provided in the region 108c are provided in parallel with each other, and the plurality of grooves 105b provided in the region 108d are also provided in parallel with each other. In addition, the groove 105a extends in a direction intersecting the groove 105b. The plurality of grooves 105a and 105b form a so-called chevron pattern in plan view.

(Female plate)

Like the male plate 100, the female plate 110 is a member that performs heat exchange between two fluids (engine oil and cooling water) flowing along the upper and lower surfaces. The female plate 110 is a metal plate material having the same size as the male plate 100. Fig. 8 is a top view of the female plate 110. The female plate 110 is formed in a substantially rectangular shape having a long side extending in the front-rear direction and a short side extending in the left-right direction in a plan view. The female plate 110 has: an upper surface 110a formed with linear grooves 115, a lower surface 110b formed with linear protrusions 114, edges 116 formed with oil inflow and outflow ports 112a, 112b, and edges 117 formed with cooling water inflow and outflow ports 113a, 113 b.

The oil inflow and outflow ports 112a, 112b are openings through which engine oil flows. The oil inflow and outflow ports 112a and 112b are provided at a set of diagonal positions among the four corners of the female plate 110. The opening sizes of the oil inflow and outflow openings 112a, 112b are the same as those of the oil inflow and outflow openings 102a, 102 b. In the present embodiment, the opening at the rear right of the female plate 110 in fig. 8 is used as the oil inflow port 112a, and the opening at the front left of the female plate 110 is used as the oil outflow port 112 b. The rim 116 of the oil inflow and outflow openings 112a, 112b protrudes downward and the lower surface thereof is planar.

The cooling water inflow outlets 113a, 113b are openings through which cooling water flows. The cooling water inflow outlets 113a, 113b are provided at a set of diagonal positions of the four corners of the female plate 110 where the oil inflow outlets 112a, 112b are not provided. In the present embodiment, the left rear opening of the female plate 110 of fig. 8 is used as the cooling water inlet 113a, and the right front opening is used as the cooling water outlet 113 b. The opening sizes of the cooling water inflow outlets 113a, 113b are the same as those of the cooling water inflow outlets 103a, 103 b. The rim 117 protrudes upward and its upper surface is planar. The shape of rim 117 corresponds to the shape of rim 107.

Here, the oil inflow and outflow ports 102a and 102b and the oil inflow and outflow ports 112a and 112b will be described. On the male plate 100, edge portions 106 forming the oil inflow and outflow ports 102a, 102b protrude upward from the upper surface 100 a. On the female plate 110, rim portions 116 forming the oil inflow openings 112a, 112b protrude downward from the upper surface 110 a. Therefore, as shown in fig. 2 (b), when the female plate 110 is superimposed on the male plate 100, the edge 106 is connected to the edge 116. The upper and lower second flow paths 132 are connected to the oil inflow and outflow ports 102a and 102b and the oil inflow and outflow ports 112a and 112 b. Accordingly, since the upper and lower second flow paths 132 are connected to each other in the second flow paths 132, all of the second flow paths 132 are connected to the oil inflow and outflow ports 102a and 102b and the oil inflow and outflow ports 112a and 112 b.

Next, the cooling water inflow outlets 103a, 103b and the cooling water inflow outlets 113a, 113b will be described. On the male plate 100, edge portions 107 forming the cooling water inflow outlets 103a, 103b protrude downward from the upper surface 100 a. On the female plate 110, rim portions 117 forming the cooling water inflow outlets 113a, 113b protrude upward from the upper surface 110 a. Therefore, as shown in fig. 2 (b), when the male plate 100 is superimposed on the female plate 110, the edge 107 is connected to the edge 117. The upper and lower first flow paths 131 are connected to the cooling water inflow outlets 103a and 103b and the cooling water inflow outlets 113a and 113 b. Therefore, since the upper and lower first flow paths 131 are connected to each other in each first flow path 131, all the first flow paths 131 are connected to the cooling water inflow outlets 103a and 103b and the cooling water inflow outlets 113a and 113 b.

Here, the cooling water inflow outlets 103a, 103b and the cooling water inflow outlets 113a, 113b are open to the first flow path 131, and the oil inflow outlets 102a, 102b and the oil inflow outlets 112a, 112b are closed to the first flow path 131. The oil inflow and outflow ports 102a and 102b and the oil inflow and outflow ports 112a and 112b are open to the second flow path 132, and the cooling water inflow and outflow ports 103a and 103b and the cooling water inflow and outflow ports 113a and 113b are closed to the second flow path 132. Therefore, the first flow path 131 is independent from the second flow path 132.

The grooves 115 are grooves that make the flow of the fluid flowing along the upper surface 110a irregular. The plurality of grooves 115 are provided so as to be recessed downward from the flat portion of the upper surface 110a, and extend linearly in a plan view. The upper surface 110a is divided into two areas 118a, 118b, and a plurality of grooves 115 are provided in each of the areas 118a, 118b.

The areas 118a and 118b are areas defined on the upper surface 110 a. The regions 118a, 118b are rectangular extending in the front-rear direction. The areas 118a, 118b are substantially symmetrically divided left and right on the upper surface 110 a. In the present embodiment, the region provided on the left side of the upper surface 110a is a region 118a, and the region provided on the right side is a region 118b.

Here, grooves 115 provided in the respective regions 118a and 118b are set as grooves 115a and 115b, respectively, for the sake of explanation. The plurality of grooves 115a provided in the region 118a are provided in parallel with each other, and the plurality of grooves 115b provided in the region 118b are also provided in parallel with each other. In addition, the groove 115a extends in a direction intersecting the groove 115b. And the plurality of grooves 115 form a so-called herringbone pattern in a plan view.

The protrusion 114 is a protrusion that makes the flow of the fluid flowing along the lower surface 110b irregular, protrudes downward from a flat portion of the lower surface 110b, and extends straight in a plan view. Fig. 9 is a bottom view of the female plate 110. The protrusion 114 is provided in plurality at the lower surface 110b. Since the protrusion 114 and the groove 115 are formed by press working, the protrusion 114 has the same shape as the groove 115 in the vertical direction. Projection 114 overlaps groove 115 in plan view. That is, each protrusion 114 is provided on the lower surface 110b in a pair with the groove 115 having the same shape. The lower surface 110b is divided into two regions 118c and 118d, and a plurality of projections 114 are provided in each region 118c and 118d.

The areas 118c and 118d are areas defined on the lower surface 110 b. The regions 118c, 118d are rectangles extending in the front-rear direction. The areas 118c, 118d are substantially symmetrically divided left and right on the lower surface 110 b. In the present embodiment, the region provided on the right side of the lower surface 110b is a region 118c, and the region provided on the left side is a region 118d. The region provided on the back surface of the region 118a is a region 118c, and the region provided on the back surface of the region 118b is a region 118d.

Here, for the sake of explanation, the protrusions 114 provided in the respective regions 118c and 118d are set as protrusions 114a and 114b, respectively. The protrusions 114a and 114b are paired with the grooves 115a and 115b of the same shape. That is, the plurality of projections 114a provided in the region 118c are provided in parallel to each other, and the plurality of projections 114b provided in the region 118d are also provided in parallel to each other. In addition, the protrusion 114a extends in a direction intersecting the protrusion 104 b. And the plurality of protrusions 114 form a so-called chevron pattern in a plan view. When the male plate 100 and the female plate 110 are stacked, the projection 114 is provided in a direction intersecting the projection 104 in a plan view.

As shown in fig. 11, the height of the protrusion 114 is about one half of the height of the space (first flow path 131) formed when the female plate 110 is overlapped on the male plate 100. The protrusion 114 is brought into contact with the joint 101, so that the protrusion 114 is joined to the protrusion 104, and the joint 111 having a dot-shaped recess recessed upward from the lower surface of the protrusion 114 is formed. The pair of the dot-shaped protrusion of the joint 101 and the dot-shaped recess of the joint 111. The joint 111 is provided at a position where the protrusion 104 intersects the protrusion 114 when the female plate 110 is superimposed on the male plate 100 in a plan view.

(Fin)

The fin 120 is a member that complicates the flow of fluid passing therethrough and exchanges heat with the fluid. The fin 120 is a metal member having a flat plate-like outer shape, in which thin plates extending in the front-rear direction, in the up-down direction, and thin plates extending in the left-right direction are combined to form a rectangular shape, and a plurality of rectangular holes are formed. As shown in fig. 11, the thickness of the fin 120 is substantially the same as the height of the space (second flow path 132) formed by the male plate 100 and the female plate 110. The upper surface of the fin 120 is in contact with the lower surface 100 b. The lower surface of the fin 120 is in contact with the upper surface 110 a.

(Top plate)

The top plate 50 is a member disposed as a member of the uppermost layer of the heat exchange portion 20. The top plate 50 is one of the female plates 110, and has a shape in which the oil inflow and outflow ports 112a and 112b and the cooling water inflow and outflow ports 113a and 113b are removed from the female plate 110. Therefore, the same reference numerals are given to the same structures as the female plate 110 in the top plate 50. The top plate 50 has: an upper surface 110a formed with linear grooves 115 and a lower surface 110b formed with linear protrusions 114. The top plate 50 is welded to the upper surface of the male plate 100, which is the uppermost member of the laminated portion 40. Thereby, the oil inflow and outflow ports 102a, 102b of the male plate 100 joined to the lower surface of the top plate 50 are closed.

(Action of oil cooler)

The operation of the oil cooler 2 will be described. Inside the oil cooler 2, cooling water flows along the first flow path 131. The engine oil flows along the second flow path 132. The first flow path 131 and the second flow path 132 are vertically adjacent to each other with the male plate 100 or the female plate 110 interposed therebetween. Accordingly, the cooling water exchanges heat with the engine oil via the male plate 100 or the female plate 110. That is, the engine oil at a high temperature is cooled by the cooling water at a low temperature. Conversely, the low-temperature cooling water is heated by the high-temperature engine oil.

(Cooling Water)

As shown by the arrow in fig. 2 (b), the cooling water is supplied from the cooling water flow path 8 to the cooling water inlet 13 a. The cooling water flows into the first flow path 131 at the lowest layer from the cooling water inlet 13 a. The cooling water flows into all the first flow paths 131 through the cooling water inlets 103a and 113 a.

As shown by arrows in fig. 12, the cooling water flows from the cooling water inlets 103a and 113a to the entire first flow path 131. The cooling water flows into the cooling water outflow ports 103b and 113 b.

A part of the cooling water flowing in contacts the protrusions 104 and 114 while flowing along the first flow path 131. Since the protrusions 104 and 114 protrude upward and downward, the cooling water in contact with the protrusions 104 and 114 flows in the upward and downward directions. Further, since the protrusions 104 and 114 are provided so as to intersect the flow direction of the cooling water, the cooling water in contact with the protrusions 104 and 114 is caused to flow in the left-right direction corresponding to the intersecting angle. Further, since the projections 104 and 114 contact at the positions of the joint portions 101 and 111, the projections 104 and 114 at the positions are columnar. Thus, a part of the cooling water is caused to flow so as to avoid the columnar projections 104 and 114. In this way, the cooling water is caused to flow in a complicated manner while flowing along the first flow path 131.

The cooling water exchanges heat with the engine oil via the male plate 100 and the female plate 110 while flowing along the first flow path 131. The surface area of the male plate 100 increases the portion where the protrusions 104 are disposed. In addition, the surface area of the female plate 110 increases by the portion where the protrusions 114 are provided. Here, the larger the area of contact between the cooling water and the member that exchanges heat with the cooling water, the higher the efficiency of heat exchange with the cooling water. Therefore, the efficiency of heat exchange with the cooling water flowing along the first flow path 131 is high.

The cooling water flows along the first flow paths 131 and flows into the cooling water outflow ports 103b and 113 b. The cooling water flows into the cooling water outflow port 13b through the cooling water outflow ports 103b, 113 b. The cooling water flows from the cooling water outflow port 13b through the cooling water flow path 8 and flows into the radiator 5.

(Engine oil)

As indicated by an arrow in fig. 2 (b), engine oil is supplied from the oil flow path 7 to the oil inflow port 12 a. The engine oil flows into the lowermost second flow path 132 from the oil inflow port 12 a. The engine oil flows into all the second flow paths 132 through the oil inlets 102a and 112 a.

As indicated by arrows in fig. 13, the engine oil flows from the oil inflow ports 102a and 112a to the entire second flow path 132. The engine oil flows into the oil outflow ports 102b and 112 b.

The inflowing engine oil contacts the fins 120 while flowing along the second flow path 132. In addition, engine oil flows through the holes formed in the fins 120 and the grooves 105 and 115. The engine oil flowing along the second flow path 132 contacts the fin 120 and flows in the grooves 105 and 115, thereby generating a flow in the left-right direction and the up-down direction.

The engine oil exchanges heat with the cooling water via the male plate 100, the female plate 110, and the fins 120 while flowing along the second flow path 132. Since the fins 120 are in contact with the lower surface 100b and the upper surface 110a, heat transfer is performed between the fins 120 and the male plate 100, and between the fins 120 and the female plate 110. That is, the fins 120 increase the area of the engine oil that is subjected to heat exchange. In addition, the surface area of the male plate 100 increases the portion where the groove 105 is provided. Likewise, the surface area of the female plate 110 increases by the portion where the grooves 115 are provided. Therefore, the efficiency of heat exchange with the engine oil flowing along the second flow path 132 is high.

The engine oil passes through the fins 120 while flowing along the second flow path 132. The fins 120 make it difficult for engine oil to flow in the second flow path 132. As a result, the pressure loss in the second flow path 132 increases. But the upper and lower surfaces of the fin 120 are in contact with the grooves 105, 115. Since the grooves 105, 115 have a larger size than the flow paths inside the fins 120, a part of the engine oil passing through the fins 120 flows from the inside of the fins 120 to the grooves 105, 115.

The engine oil flows along each second flow path 132 and flows into the oil outflow ports 102b, 112 b. Engine oil flows into the oil outflow port 12b through the oil outflow ports 102b, 112 b. The engine oil flows from the oil outflow port 12b through the oil flow path 7 and into the oil pump 4.

(Effect)

In the above embodiment, the oil cooler 2 includes a plate (male plate 100 or female plate 110) having an upper surface 100a or a lower surface 110b to be contacted by the cooling water, and a plurality of protrusions 104 and 114 extending linearly are formed on the upper surface 100 a.

Since the protrusions 104, 114 contacting the cooling water are formed on the plate, the contact area of the cooling water with the plate is increased. The larger the contact area of the cooling water with the plate in contact with the cooling water at the time of heat exchange, the higher the efficiency of heat exchange by the cooling water, and thus the efficiency of heat exchange by the oil cooler 2 is improved.

In addition, since the cooling water contacts the protrusion 104, the flow of the cooling water varies along the protrusion 104. Therefore, the flow of the cooling water is in a complicated state. The more complicated the flow of the cooling water, the higher the efficiency of heat exchange by the cooling water, and thus the efficiency of heat exchange by the oil cooler 2 is improved.

The plurality of protrusions 104 and 114 of the oil cooler 2 of the present embodiment extend so as to intersect the flow direction of the cooling water.

Since the plurality of projections 104 and 114 extend so as to intersect the flow direction of the cooling water, when the cooling water contacts the projections 104 and 114, the flow of the cooling water corresponding to the angle at which the flow direction of the cooling water intersects the projections 104 and 114 is generated. Therefore, the efficiency of heat exchange is improved because the cooling water is caused to flow in a complex manner.

The upper surface 100a or the lower surface 110b of the oil cooler 2 of the present embodiment is divided into a region 108a and a region 108b or a region 118c and a region 118d, which extend in the flow direction of the cooling water, respectively, and the projections 104a in the region 108a and the projections 104b in the region 108b or the projections 114a in the region 118c and the projections 114b in the region 118d of the plurality of projections 104, 114 extend in the direction intersecting each other.

The upper surface 100a or the lower surface 110b is divided into a region 108a and a region 108b or a region 118c and a region 118d extending in the flow direction of the cooling water, respectively, and the protrusion 104a in the region 108a and the protrusion 104b in the region 108b or the protrusion 114a in the region 118c and the protrusion 114d in the region 118d of the protrusions 104, 114 extend in the direction intersecting each other, so that the flow direction of the cooling water flowing in the region 108a is different from the flow direction of the cooling water flowing in the region 108 b. Or the flow direction of the cooling water flowing in the region 118c is made different from the flow direction of the cooling water flowing in the region 118 d. Therefore, since the cooling water is caused to flow in a complicated manner, the efficiency of heat exchange is improved.

The plate of the oil cooler 2 of the present embodiment further includes: a lower surface 100b on the opposite side of the upper surface 100a or an upper surface 110a on the opposite side of the lower surface 110b, which are in contact with engine oil for heat exchange with cooling water, are formed with a plurality of grooves 105, 115 extending linearly on the lower surface 100b or the upper surface 110 a.

The plate includes a lower surface 100b or an upper surface 110a on the opposite side of the upper surface 100a or on the opposite side of the lower surface 110b, which is in contact with engine oil for heat exchange with cooling water, and a plurality of grooves 105 and 115 extending linearly are formed in the lower surface 100b or the upper surface 110a, so that the lower surface 100b or the upper surface 110a has a wave shape. Therefore, the contact area of the engine oil with the plate increases. The larger the contact area of the engine oil with the parts in contact with the engine oil when heat exchange is performed, the higher the efficiency of heat exchange with the engine oil, and thus the efficiency of heat exchange with the oil cooler 2 is improved.

In addition, since the lower surface 100b or the upper surface 110a has a wave-like shape, engine oil flows along the grooves 105, 115. As a result, the engine oil is caused to flow in a complicated manner, and therefore, the efficiency of heat exchange is improved.

The cooling water and the engine oil exchange heat via the plate. Not only the efficiency of heat exchange with the upper surface 100a or the lower surface 110b by the cooling water but also the efficiency of heat exchange with the lower surface 100b or the upper surface 110a by the engine oil is improved, and thus the efficiency of heat exchange with the oil cooler 2 as a whole is improved.

The plurality of grooves 105 and 115 of the oil cooler 2 of the present embodiment extend so as to intersect the flow direction of the engine oil.

Since the plurality of grooves 105, 115 extend so as to intersect the flow direction of the engine oil, when the engine oil flows along the grooves 105, 115, a flow of the engine oil corresponding to an angle at which the flow direction of the engine oil intersects the grooves 105, 115 is generated. Thus, the engine oil is caused to flow in a complicated manner, and thus the efficiency of heat exchange is improved.

The lower surface 100b or the upper surface 110a of the oil cooler 2 of the present embodiment is divided into a region 108c and a region 108d, or a region 118a and a region 118b, which extend in the flow direction of the engine oil, respectively, and the grooves 105a in the region 108c and the grooves 105b in the region 108d, or the grooves 115a in the region 118a and the grooves 115b in the region 118b of the plurality of grooves 105, 115 extend in the direction intersecting each other.

The lower surface 100b or the upper surface 110a is divided into a region 108c and a region 108d or a region 118a and a region 118b, respectively, extending in the flow direction of the engine oil, and the grooves 105a in the region 108c and the grooves 105b in the region 108d or the grooves 115a in the region 118a and the grooves 115b in the region 118b extend in the direction intersecting each other, so that the flow direction of the engine oil flowing in the region 108c is different from the flow direction of the engine oil flowing in the region 108 d. Or the direction of the engine oil flowing in the region 118a is made different from the direction of the engine oil flowing in the region 118 b. Thus, the engine oil is caused to flow in a complicated manner, and thus the efficiency of heat exchange is improved.

The oil cooler 2 of the present embodiment further includes a fin 120, and the fin 120 is in contact with at least one of the plurality of protrusions 104 and any one of the lower surface 100b or in contact with at least one of the plurality of protrusions 114 and any one of the upper surface 110a, and diffuses the flow of the cooling water or the engine oil.

The flow of the cooling water or the engine oil is diffused by the fin 120, and the fin 120 is in contact with at least one of the plurality of protrusions 104 and any one of the lower surface 100b, or in contact with at least one of the plurality of protrusions 114 and any one of the upper surface 110a, and at least one of the plurality of protrusions 114. Therefore, the portion where the cooling water or the engine oil contacts the plate is increased, thereby increasing the amount of heat exchange between the cooling water or the engine oil and the plate. As a result, the efficiency of heat exchange of the entire oil cooler 2 is improved.

Further, since the fin 120 is in contact with either the protrusion 104 or the lower surface 100b or either the protrusion 114 or the upper surface 110a, the fin 120 is in contact with the plate. Therefore, a member that exchanges heat with the cooling water or the engine oil is increased. As a result, the efficiency of heat exchange of the entire oil cooler 2 is improved.

Further, the fins 120 improve the efficiency of heat exchange as described above. On the other hand, the fin 120 increases the resistance in the flow path of the cooling water or the engine oil, and thus increases the pressure loss in the flow path. Here, since the fin 120 is in contact with either the protrusion 104 or the lower surface 100b, the fin 120 is in contact with the groove formed between the protrusions 104 or the groove 105 formed on the lower surface 100b at the contact portion. Since the fin 120 is in contact with either the protrusion 114 or the upper surface 110a, the fin 120 is in contact with the groove formed between the protrusions 114 or the groove 115 formed in the upper surface 110a at the contact portion. Since these grooves function as flow paths for cooling water or engine oil, the pressure loss in the flow paths is reduced. That is, the following effects can be obtained: the increase in pressure loss in the flow path is suppressed, and the efficiency of heat exchange by the fins 120 is improved.

The plurality of protrusions 104 and 114 of the oil cooler 2 of the present embodiment overlap the plurality of grooves 105 and 115 in the orthogonal direction of the upper surface 100a or the lower surface 110 b.

Since the plurality of protrusions 104, 114 overlap the plurality of grooves 105, 115 as viewed in the orthogonal direction of the upper surface 100a or the lower surface 110b, the protrusions 104 and the grooves 105 or the protrusions 114 and the grooves 115 are at the same position on the surface or the back of the plate. Here, in order to provide the grooves 105 and 115 on the lower surface 100b or the upper surface 110a, the thickness of the plate needs to be larger than the depth of the grooves 105 and 115. However, if the protrusion 104 and the groove 105 or the protrusion 114 and the groove 115 are at the same position on the front or rear surface of the plate, the groove 105 can be provided from the lower surface 100b with respect to the protruding portion of the protrusion 104 or the groove 115 can be provided from the upper surface 110a with respect to the protruding portion of the protrusion 114, and thus the plate can be thinned. As a result, the oil cooler 2 becomes thin.

The oil cooler 2 of the present embodiment further includes a plate having a lower surface 110b or an upper surface 100a to which cooling water is brought into contact, and a plurality of protrusions 114 and 104 extending linearly are formed on the lower surface 110b or the upper surface 100a, and the upper surface 100a faces the lower surface 110 b.

The oil cooler 2 includes a plate having a lower surface 110b or an upper surface 100a to which cooling water is brought into contact, and a plurality of protrusions 114, 104 extending linearly are formed on the lower surface 110b or the upper surface 100 a. Here, since the upper surface 100a and the lower surface 110b face each other, the cooling water flows between the upper surface 100a and the lower surface 110 b. Accordingly, since the cooling water contacts not only the protrusion 104 but also the protrusion 114, more complicated flow of the cooling water is generated. As a result, the efficiency of heat exchange is improved.

In addition, at least one protrusion 104 of the plurality of protrusions 104 of the oil cooler 2 of the present embodiment is in contact with the plurality of protrusions 114.

Since at least one protrusion 104 of the plurality of protrusions 104 is in contact with the plurality of protrusions 114, the contact portions of the two protrusions form a column or wall between the upper surface 100a and the lower surface 110 b. Thus, the cooling water flows in a manner avoiding the column or the wall, thereby generating a more complicated flow of the cooling water. As a result, the efficiency of heat exchange is improved.

In addition, since the column or the wall is formed between the plates, the oil cooler 2 has high strength against the force acting in the plate opposing direction.

In addition, the plurality of protrusions 104 of the oil cooler 2 of the present embodiment extend in directions intersecting the plurality of protrusions 114, respectively.

Since the plurality of protrusions 104 extend in directions intersecting the plurality of protrusions 114, respectively, the direction of the wave-like shape formed on the upper surface 100a is made different from the direction of the wave-like shape formed on the lower surface 110 b. Therefore, when the cooling water flows between the upper surface 100a and the lower surface 110b, the cooling water generates a complicated flow. As a result, the efficiency of heat exchange is improved.

(Modification)

The following modifications can be applied in combination.

(1) Modification 1

There are the following cases: when the heat exchange system 1 is just after the start of operation or the like, the temperature of the engine oil is lower than the temperature of the cooling water. At this time, the oil cooler 2 exchanges heat between the engine oil at a low temperature and the water at a high temperature. As a result, the engine oil is heated and cooled with water.

(2) Modification 2

The structure of the heat exchange system 1 may be different. For example, the oil pump 4 and the water pump 6 may be disposed at different positions. The engine 3 may be replaced with a transmission or an electric motor. In this case, the engine oil is replaced with transmission oil or motor oil.

(3) Modification 3

The fluid in heat exchange with the water may be a gas. For example, the oil cooler 2 serves as EGR

(Exhaust Gas Recirculation: exhaust gas recirculation) the EGR system, which recirculates exhaust gas from the engine 3, to be mixed with intake gas of the engine 3, functions. The EGR cooler takes in a part of the exhaust gas discharged from the engine 3, exchanges heat between the exhaust gas and water, and cools the exhaust gas. The exhaust gas cooled by the EGR cooler is mixed with the intake gas of the engine 3. In this case, the heat exchanging system 1 eliminates the oil pump 4, and the oil passage 7 becomes a gas passage.

(4) Modification 4

The flow direction of the engine oil and the cooling water may be different. That is, in the present embodiment, the engine oil flows from the oil flow path 7 through the oil inflow port 12a, the oil inflow port 112a, the second flow path 132, the oil outflow port 112b, and the oil outflow port 12b in this order, but the engine oil may also flow from the oil flow path 7 through the oil outflow port 12b, the oil outflow port 112b, the second flow path 132, the oil inflow port 112a, and the oil inflow port 12a in this order. Similarly, the cooling water may flow from the cooling water flow path 8 through the cooling water outflow port 13b, the cooling water outflow port 103b, the first flow path 131, the cooling water inflow port 103a, and the cooling water inflow port 13a in this order.

(5) Modification 5

The plurality of protrusions 104, 114 may not extend so as to intersect the flow direction of the cooling water, respectively. In this case, at least one protrusion 104, 114 of the plurality of protrusions 104, 114 extends parallel to the flow direction of the cooling water.

(6) Modification 6

Regarding the upper surface 100a or the lower surface 110b, it may be that the region 108a and the region 108b or the region 118c and the region 118d, respectively, extending in the flow direction of the cooling water are not divided, and it may be that the protrusion 104a in the region 108a and the protrusion 104b in the region 108b or the protrusion 114a in the region 118c and the protrusion 114b in the region 118d, among the plurality of protrusions 104 or the protrusions 114, do not extend in the direction intersecting each other. In this case, the upper surface 100a or the lower surface 110b is not divided into two areas. The plurality of protrusions 104 and 114 may extend parallel to each other or may extend in directions intersecting each other on the upper surface 100a and the lower surface 110 b.

(7) Modification 7

The plate may not have a plurality of grooves 105 or grooves 115 extending in a linear shape formed on the lower surface 100b or the upper surface 110 a. In this case, the lower surface 100b or the upper surface 110a may be a plane. The lower surface 100b or the upper surface 110a may be embossed, or protrusions or bosses may be provided.

(8) Modification 8

The plurality of grooves 105, 115 may not extend so as to intersect the flow direction of the engine oil, respectively. In this case, at least one groove 105, 115 of the plurality of grooves 105, 115 extends parallel to the flow direction of the engine oil.

(9) Modification 9

Regarding the lower surface 100b or the upper surface 110a, it may be that the region 108c and the region 108d, or the region 118a and the region 118b, respectively, extending in the flow direction of the engine oil are not divided, and it may be that the groove 105a in the region 108c and the groove 105b in the region 108d, or the groove 115a in the region 118a and the groove 115b in the region 118b, of the plurality of grooves 105 or the grooves 115, do not extend in the direction intersecting each other. In this case, the lower surface 100b or the upper surface 110a is not divided into two areas. The plurality of grooves 105 and 115 may extend parallel to each other or in directions intersecting each other on the lower surface 100b and the upper surface 110 a.

(10) Modification 10

The oil cooler 2 may not have the fins 120 in contact with the lower surface 100b or the upper surface 110 a. In this case, the fins 120 are not provided in the second flow path 132.

(11) Modification 11

The oil cooler 2 may be provided with fins 120 in contact with the protrusions 104, 114. In this case, for example, the height of the protrusions 104 and 114 and the height of the fin 120 are changed, and the fin 120 is provided in the first flow path 131 so as to be in contact with the protrusions 104 and 114.

(12) Modification 12

The plurality of protrusions 104, 114 may not overlap the plurality of grooves 105, 115 as viewed in the orthogonal direction of the upper surface 100a or the lower surface 110 b. In this case, the plurality of protrusions 104, 114 are offset from the plurality of grooves 105, 115 as viewed in the orthogonal direction of the upper surface 100a or the lower surface 110b, and thus the plate is thickened by an amount corresponding to the depth of the grooves 105, 115.

(13) Modification 13

The oil cooler 2 may include only one of the male plate 100 and the female plate 110. For example, the stacked portion 40 may be formed by alternately stacking the male plate 100 and the plate other than the female plate 110 in the up-down direction, or may be formed by alternately stacking the female plate 110 and the plate other than the male plate 100 in the up-down direction.

(14) Modification 14

The plurality of protrusions 104, 114 may not be in contact with the plurality of protrusions 114, 104. In this case, for example, the height of the plurality of projections 104, 114 is lower than half the height of the first flow path 131 and the second flow path 132.

(15) Modification 15

The plurality of protrusions 104, 114, respectively, may not extend in a direction intersecting the plurality of protrusions 114, 104. In this case, at least one protrusion 104 of the plurality of protrusions 104, 114,

114 Extend parallel to the plurality of protrusions 114, 104.

(16) Modification 16

The plurality of protrusions 104, 114 and the plurality of grooves 105, 115 may not be linear. The line formed by the plurality of protrusions 104, 114 and the plurality of grooves 105, 115 includes a curved line and a broken line in addition to the straight line. Accordingly, the plurality of protrusions 104, 114 and the plurality of grooves 105, 115 may be curved or folded. The fold line shape is, for example, a V-shape, an inverted V-shape, an X-shape, or the like, and includes a combination of these shapes.

(17) Modification 17

The plurality of protrusions 104, 114 and the grooves 105, 115 may be formed of a plurality of wires. In this case, for example, the plurality of projections 104 and 114 and the plurality of grooves 105 and 115 are formed of straight lines and curved lines on one plate.

(18) Modification 18

In the present embodiment, the engine oil and the cooling water flow into the oil cooler 2 or out of the oil cooler 2 through the oil inflow and outflow ports 12a and 12b and the cooling water inflow and outflow ports 13a and 13b, but other configurations than the above are also possible. For example, as shown in fig. 14, oil inflow and outflow ports 52a and 52b and cooling water inflow and outflow ports 53a and 53b may be provided in the top plate 50. The oil inflow/outflow ports 52a and 52b and the cooling water inflow/outflow ports 53a and 53b are tubular members, and are attached to openings provided at four corners of the top plate 50, and the member attached to the rear right is the oil inflow port 52a, the member attached to the front left is the oil outflow port 52b, the member attached to the rear left is the cooling water inflow port 53a, and the member attached to the front right is the cooling water outflow port 53b in plan view. The oil inflow and outflow ports 52a and 52b are connected to the oil flow path 7, and form a flow path for engine oil. Similarly, the cooling water inflow outlets 53a and 53b are connected to the cooling water flow path 8, and form a cooling water flow path.

(19) Modification 19

In the present embodiment, the plurality of projections 104 and 114 and the grooves 105 and 115 are provided in the rectangular areas 108a, 108b, 108c, 108d, 118a, 118b, 118c, 118d, but may be provided in other areas of the upper surfaces 100a and 110a and the lower surfaces 100b and 110b than the above. For example, in the male plate 100, the oil inflow and outflow ports 102a and 102b and the cooling water inflow and outflow ports 103a and 103b are smaller in size in the lateral direction only, and are disposed at the lateral direction end portions of the male plate 100, respectively. In this case, flat portions are formed between the oil inflow port 102a and the cooling water inflow port 103a and between the oil outflow port 102b and the cooling water outflow port 103b on the upper surface 100a and the lower surface 100 b. Projections 104 and grooves 105 are provided in these planar portions.

(20) Modification 20

In the present embodiment, the regions 108a, 108b, 108c, 108d, 118a, 118b, 118c, 118d are rectangular, but may be square.

(21) Modification 21

In the present embodiment, the dimension of the angle formed by the intersection of the protrusions 104a and 104b with respect to the straight line extending in the front-rear direction as the center line in plan view is the same as the dimension of the angle formed by the intersection of the protrusions 114a and 114b with respect to the straight line extending in the front-rear direction as the center line in plan view, but may be different. For example, the dimension of the angle formed by the projections 104a and 104b intersecting each other is set to 30 degrees with respect to a straight line extending in the front-rear direction as a center line in a plan view, and the projection 114a with respect to the straight line extending in the front-rear direction as a center line in a plan view

The angle formed by the intersection with 114b is set to 120 degrees.

Description of the reference numerals

2-Oil cooler (heat exchanger); 100-male plate (first plate); 100 a-upper surface (first surface); 100 b-lower surface (opposite surface); 104-protrusion (first protrusion); 105-slot;

108 a-region (first region); 108 b-region (second region); 108 c-region (third region); 108 d-region (fourth region); 110-female plate (second plate); 110 a-lower surface (second surface); 114-protrusion (second protrusion); 120-fins (diffusion members).

Claims (11)

1. A heat exchanger is provided with a first plate,

The first plate has a first surface to be in contact with a heat supply medium, and a plurality of first protrusions extending in a linear shape are formed on the first surface.

2. A heat exchanger according to claim 1 wherein,

The plurality of first protrusions extend so as to intersect the flow direction of the heat medium, respectively.

3. A heat exchanger according to claim 1 or 2, wherein,

The first surface is divided into a first region and a second region extending in a flow direction of the heat medium,

The protrusions within the first region and the protrusions within the second region of the plurality of first protrusions extend in directions intersecting each other.

4. A heat exchanger according to any one of claims 1 to 3 wherein,

The first plate further having opposite sides for heat exchanging fluid with the heat medium, on opposite sides of the first surface,

A plurality of grooves extending linearly are formed in the opposite surfaces.

5. The heat exchanger of claim 4, wherein the heat exchanger is configured to heat the heat exchanger,

The plurality of grooves extend so as to intersect with the flow direction of the fluid.

6. A heat exchanger according to claim 4 or 5, wherein,

The opposite faces are divided into a third region and a fourth region extending in the flow direction of the fluid respectively,

The grooves in the third region and the grooves in the fourth region of the plurality of grooves extend in directions intersecting each other.

7. A heat exchanger according to any one of claims 4 to 6 wherein,

The heat medium or fluid flow diffusing device further includes a diffusing member that is in contact with at least one of the first protrusions and one of the opposite surfaces of the plurality of first protrusions, and diffuses the heat medium or fluid flow.

8. A heat exchanger according to any one of claims 4 to 7 wherein,

The plurality of first protrusions overlap the plurality of grooves as viewed in the orthogonal direction of the first surface.

9. A heat exchanger according to any one of claims 1 to 8 wherein,

The heat exchanger further comprises a second plate having a second surface for contacting the heat medium, a plurality of second protrusions extending linearly are formed on the second surface,

The first surface is opposite the second surface.

10. A heat exchanger according to claim 9 wherein,

At least one of the first protrusions is in contact with the second protrusions.

11. A heat exchanger according to claim 9 or 10, wherein,

The plurality of first protrusions extend in a direction intersecting the plurality of second protrusions, respectively.