HEAT EXCHANGER

TECHNICAL FIELD

The present disclosure relates to a heat exchanger.

BACKGROUND ART

There are heat exchangers in which a plurality of plate members are stacked such that flow paths through which gas or oil flows and flow paths through which cooling water flows are formed alternately in the stacking direction of the plate members (PTL 1).

CITATION LIST
Patent Literature

- [PTL 1] Japanese Patent No. 4527557

SUMMARY OF INVENTION
Technical Problem

In the heat exchanger of PTL 1, the first flow path is embossed and provided with protrusions, however, there is a demand for heat exchangers with even higher heat exchange performance.

Thus, the present disclosure is achieved in view of circumstances described above, and is directed to provision of a heat exchanger with high heat exchange performance.

Solution to Problem

To address an issue described above, provided is a heat exchanger having a first surface configured to contact a heat medium, the first surface having a plurality of first protrusions extending linearly formed at the first surface.

Advantageous Effects of Invention

According to a heat exchanger according to the present disclosure, the performance of heat exchange is improved.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a schematic diagram illustrating a heat exchange system 1.

FIG. 2 is a perspective view of an oil cooler 2.

FIG. 3 is an exploded view of an oil cooler 2.

FIG. 4 is an exploded view of a plate assembly 60.

FIG. 5 is an exploded view of a joint section in which two plate assemblies 60 are stacked.

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

FIG. 7 is a bottom view of a male plate 100.

FIG. 8 is a top view of a female plate 110.

FIG. 9 is a bottom view of a female plate 110.

FIG. 10 is a top view of a plate assembly 60.

FIG. 11 is a sectional view of a plate assembly 60.

FIG. 12 is a schematic diagram illustrating a flow of cooling water.

FIG. 13 is a schematic diagram illustrating a flow of oil.

FIG. 14 is a perspective view of an oil cooler 2 in Modification 18.

DESCRIPTION OF EMBODIMENTS

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

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 the high temperature engine oil discharged from the engine 3 and the 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 connects the engine 3 and the oil cooler 2, the oil cooler 2 and the oil pump 4, and the oil pump 4 and the engine 3, with piping, and allows the engine oil to circulate therethrough in the direction of the arrows in FIG. 1.

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

The cooling water flow path 8 is a flow path through which cooling water flows. The cooling water flow path 8 connects the radiator 5 and the water pump 6, the water pump 6 and the oil cooler 2, and the oil cooler 2 and the radiator 5, with piping, and allows the cooling water to circulate in the direction of the arrows in FIG. 1.

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

FIG. 2A is a perspective view of the oil cooler 2. The oil cooler 2 includes a bottom flange 10 and a heat exchange unit 20.

(Bottom Flange)

The bottom flange 10 is a member for attaching the oil cooler 2 to another structure such as an engine block or the like. The bottom flange 10 is a metal plate. The bottom flange 10 has a plurality of through holes 11, oil inlet/outlet 12a, 12b, and cooling water inlet/outlet 13a, 13b. FIG. 3 is an exploded view of the oil cooler 2.

A vertical direction is defined as the direction parallel to the thickness of the bottom flange 10. In addition, as illustrated in FIG. 3 and the like, a front-rear direction is defined as the direction orthogonal to the vertical direction, and a left-right direction is defined as the direction orthogonal to the vertical and front-rear directions.

The through holes 11 are holes for fixing with a screw. Such a through hole 11 is a hole passing through the bottom flange 10 vertically. The through hole 11 is formed at the outer peripheral edge part of the bottom flange 10 so as not to overlap the attachment part of the heat exchanger 20. In an embodiment of the present disclosure, the bottom flange 10 has six through holes 11. The oil cooler 2 is attached to another structure by fitting bolts (not shown) into the through holes 11 and fastening the bolts to the other structure.

The oil inlet/outlet 12a, 12b are openings through which the engine oil is to flow. In an embodiment of the present disclosure, the rear opening of the bottom flange 10 is used as the oil inlet 12a, and the front opening is used as the oil outlet 12b.

The cooling water inlet/outlet 13a, 13b are openings through which the cooling water is to flow. In an embodiment of the present disclosure, 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 13b. The cooling water inlet 13a has a small diameter opening 14a and a large diameter opening 15a. The small diameter opening 14a is provided from the bottom surface of the bottom flange 10 toward the top surface, to be connected to the large diameter opening 15a. The large diameter opening 15a is provided from the small diameter opening 14a upward to the upper surface of the bottom flange 10. The large diameter opening 15a is larger than the small diameter opening 14a when viewed from above, and is provided such that the small diameter opening 14a is arranged inside the large diameter opening 15a. The cooling water outlet 13b has a small diameter opening 14b and a 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 Unit)

A heat exchange unit 20 is a structure that forms separate flow paths for the engine oil and the cooling water that are fluids, and that exchanges heat between the two fluids flowing through the respective flow paths. The heat exchange unit 20 includes a bottom plate 30, a stacked section 40, and a top plate 50. The heat exchange unit 20 is obtained such that the stacked section 40 is stacked on the upper surface of the bottom plate 30, and the top plate 50 is further stacked on the upper surface of the stacked section 40.

(Bottom Plate)

The bottom plate 30 is a member disposed at the lowest layer of the heat exchange unit 20 and attached to the bottom flange 10. The bottom plate 30 is attached to the lower surface of the lowest plate of the stacked section 40. In an embodiment of the present disclosure, the bottom plate 30 is a male plate 100, which will be described later.

(Stacked Section)

The stacked section 40 is a structure in which plate members are stacked in the vertical direction to form separate paths for the engine oil and the cooling water. The stacked section 40 is obtained such that a plurality of plate assemblies 60 are stacked and joined together by brazing. In an embodiment of the present disclosure, the stacked section 40 is a stack of four plate assemblies 60.

(Plate Assembly)

The plate assembly 60 includes a male plate 100, a female plate 110, and a fin 120. FIG. 4 is an exploded view of the plate assembly 60. The plate assembly 60 is obtained by stacking such that the male plate 100 is arranged on the upper side, the female plate 110 is arranged on the lower side, and the fin 120 is arranged therebetween. A space is formed inside the plate assembly 60 by the male plate 100 and the female plate 110, and functions as a second flow path 132 through which the engine oil is to flow.

FIG. 5 is a diagram in which the female plate 110 is arranged on the upper side, and the male plate 100 is arranged on the lower side. When the two plate assemblies 60 are stacked, the female plate 110 and the male plate 100 are arranged as illustrated in FIG. 5, in a joint section. A space is formed by the female plate 110 and the male plate 100 in the joint section of the two plate assemblies 60, and functions as a first flow path 131 through which the cooling water is to flow.

(Structure of Oil Cooler Flow Path)

FIG. 2B is a simplified cross-sectional view at a position IIb of FIG. 2A. The bottom plate 30 is provided to the top surface of the bottom flange 10. On the bottom plate 30, the female plates 110 and the male plates 100 are alternately arranged in the vertical direction.

A space formed by providing the female plate 110 onto the male plate 100 is the first flow path 131. A space formed by providing the male plate 100 on the female plate 110 is the second flow path 132. The first and second flow paths 131 and 132 are formed alternately in the vertical direction. The first flow path 131 and the second flow path 132 are formed of spaces partitioned by the male plates 100 and the female plates 110, and thus are independent from each other.

The cooling water flows 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 outlet 13b. The cooling water flows out from the cooling water outlet 13b to the radiator 5.

The engine oil flows from the oil inlet 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 outlet 12b to the oil pump 4.

(Male Plate)

The male plate 100 is a member that exchanges heat between two fluids (the engine oil, the cooling water) flowing along its upper surface and its lower surface, respectively. The male plate 100 is a metal plate that is one size smaller than the bottom flange 10. FIG. 6 is a top view of the male plate 100. The male plate 100 is formed in a substantially rectangular shape with long sides extending in the front-rear direction and short sides extending in the left-right direction, when viewed from above. The male plate 100 has an upper surface 100a where linear protrusions 104 are formed, a lower surface 100b where linear grooves 105 are formed, edge parts 106 where oil inlet/outlet 102a, 102b are formed, edge parts 107 where cooling water inlet/outlet 103a, 103b are formed.

The oil inlet/outlet 102a, 102b are openings through which the engine oil is to flow. The oil inlet/outlet 102a, 102b are provided at a pair of diagonal positions among the four corners of the male plate 100. The size of the openings of the oil inlet/outlet 102a, 102b are larger than that of the oil inlet/outlet 12a, 12b of the bottom flange 10. In an embodiment of the present disclosure, the right rear opening of the male plate 100 in FIG. 6 is used as the oil inlet 102a, and the left front opening of the male plate 100 is used as the oil outlet 102b. The edge parts 106 of the oil inlet and outlet 102a, 102b protrude upward, and have flat upper surfaces.

The cooling water inlet/outlet 103a, 103b are openings through which the cooling water is to flow. The cooling water inlet/outlet 103a, 103b are provided at a pair of diagonal positions where the oil inlet and outlet 102a, 102b are not provided among the four corners of the male plate 100. In an embodiment of the present disclosure, the rear left opening of the male plate 100 in FIG. 6 is used as the cooling water inlet 103a, and the right front opening is used as the cooling water outlet 103b. The size of the openings of the cooling water inlet and outlet 103a, 103b is the same as that of the large diameter openings 15a and 15b. The edge parts 107 protrude downward and have flat lower surfaces. The shape of the edge parts 107 matches the shape of the large diameter openings 15a and 15b. Further, the length of the edge parts 107 protruding downward matches the depth of the large diameter openings 15a, 15b.

The protrusions 104 are protrusions to disturb the flow of the fluid flowing along the upper surface 100a, and protrudes upward from a flat part of the upper surface 100a, and extends linearly when viewed from above. The plurality of protrusions 104 are provided to the upper surface 100a. The upper surface 100a is divided into two regions 108a and 108b, and the plurality of protrusions 104 are provided in each of the regions 108a and 108b.

The regions 108a and 108b are regions provided by dividing the upper surface 100a. The regions 108a and 108b each have a rectangular shape extending in the front-rear direction. The regions 108a and 108b are obtained by dividing the upper surface 100a substantially symmetrically in the left-right direction. In an embodiment of the present disclosure, the region provided on the left side of the upper surface 100a is the region 108a, and the region provided on the right side is the region 108b.

Here, for the sake of explanation, the protrusions 104 provided in the region 108a and the protrusions 104 provided in the region 108b will be referred to as protrusions 104a and 104b, respectively. The plurality of protrusions 104a provided within the region 108a are arranged so as to be parallel to each other, and the plurality of protrusions 104b provided within the region 108b are also arranged so as to be parallel to each other. Further, the protrusions 104a extend in the direction intersecting the extending direction of the protrusions 104b. Note that the plurality of protrusions 104a and 104b form a so-called herringbone pattern when viewed from above.

As illustrated in FIG. 11, the height of the protrusions 104 is about half the height of the space (the first flow path 131) formed when the female plate 110 is stacked on the male plate 100. The protrusions 104 have joint parts 101 which are dot-shaped protrusions. The joint parts 101 are each provided at a position at which the protrusion 104 and a protrusion 114 intersect when the female plate 110 is stacked on the male plate 100 when viewed from above.

The grooves 105 are grooves to disturb the flow of the fluid flowing along the lower surface 100b. 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 a flat part of the lower surface 100b, and each extends linearly when viewed from below. Since the grooves 105 and the protrusions 104 are formed by press working, the grooves 105 have the same shape as the shape of the protrusions 104 when viewed in the vertical direction. The grooves 105 are aligned with the protrusions 104 when viewed from below. In other words, the grooves 105 are provided at the lower surface so as to be paired with the respective protrusions 104 having the same shapes, respectively. The lower surface 100b is divided into two regions 108c and 108d, and the plurality of grooves 105 are provided in each of the region 108c and 108d.

The regions 108c and 108d are regions provided by dividing the lower surface 100b. The regions 108c and 108d each have a rectangular shape extending in the front-rear direction. The regions 108c and 108d are obtained by dividing the lower surface 100b substantially symmetrically in the left-right direction. In an embodiment of the present disclosure, the region provided on the right side in the lower surface 100b is the region 108c, and the region provided on the left side is the region 108d. Further, the region provided at the back surface of the region 108a is the region 108c, and the region provided at the back surface of the region 108b is the region 108d.

Here, for the sake of explanation, the grooves 105 provided in the region 108c and the grooves 105 provided in the region 108d will be referred to as grooves 105a and 105b, respectively. The grooves 105a, 105b are respectively paired with the protrusions 104a, 104b having the same shapes, respectively. The plurality of grooves 105a provided in the region 108c are arranged so as to be parallel to each other, and the plurality of grooves 105b provided in the region 108d are also provided so as to be parallel to each other. Further, the grooves 105a extend in the direction intersecting the extending direction of the grooves 105b. Note that the plurality of grooves 105a and 105b form a so-called herringbone pattern when viewed from below.

(Female Plate)

The female plate 110, similarly to the male plate 100, is a member that exchanges heat between two fluids (the engine oil, the cooling water) 1 flowing along its upper surface and its upper lower surface, respectively. The female plate 110 is a metal plate having the same size as that of 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 with long sides extending in the front-rear direction and short sides extending in the left-right direction, when viewed from above. The female plate 110 has an upper surface 110a where linear grooves 115 are formed, a lower surface 110b where linear protrusions 114 are formed, edge parts 116 where oil inlet/outlet 112a, 112b are formed, and edge parts 117 where cooling water inlet/outlet 113a, 113b are formed.

The oil inlet/outlet 112a, 112b are openings through which the engine oil is to flow. The oil inlet/outlet 112a, 112b are provided at a pair of diagonal positions among the four corners of the female plate 110. The size of the openings of the oil inlet/outlet 112a, 112b is the same as that of the oil inlet/outlet 102a, 102b. In an embodiment of the present disclosure, the right rear opening of the female plate 110 in FIG. 8 is used as the oil inlet 112a, and the left front opening of the female plate 110 is used as the oil outlet 112b. The edge parts 116 of the oil inlet and outlet 112a, 112b protrude downward, and have flat lower surfaces.

The cooling water inlet and outlet 113a, 113b are openings through which the cooling water is to flow. The cooling water inlet and outlet 113a, 113b are provided at a pair of diagonal positions where the oil inlet and outlet 112a, 112b are not provided among the four corners of the female plate 110. In an embodiment of the present disclosure, the rear left opening of the female plate 110 in FIG. 8 is used as the cooling water inlet 113a, and the right front opening is used as the cooling water outlet 113b. The size of the openings of the cooling water inlet and outlet 113a, 113b is the same as that of the cooling water inlet and outlet 103a, 103b. The edge parts 117 protrude upward, and have flat upper surfaces. The shape of the edge parts 117 matches the shape of the edge parts 107.

Here, the oil inlet and outlet 102a, 102b and the oil inlet and outlet 112a, 112b will be described. In the male plate 100, the edge parts 106 forming the oil inlet and outlet 102a, 102b protrude upward from the upper surface 100a. In the female plate 110, the edge parts 116 forming the oil inlet and outlet 112a, 112b protrude downward from the upper surface 110a. Thus, as illustrated in FIG. 2B, when the female plate 110 is stacked on the male plate 100, the edge parts 106 and 116 are coupled. Further, the upper and lower second flow paths 132 are connected through the oil inlet and outlet 102a, 102b and the oil inlet and outlet 112a, 112b. Accordingly, in the respective second flow paths 132, the upper and lower second flow paths 132 are connected, and thus all the second flow paths 132 are connected through the oil inlet and outlet 102a, 102b and the oil inlet and outlet 112a, 112b.

Next, the cooling water inlet and outlet 103a, 103b and the cooling water inlet and outlet 113a, 113b will be described. In the male plate 100, the edge parts 107 forming the cooling water inlet and outlet 103a, 103b protrude downward from the upper surface 100a. In the female plate 110, the edge parts 117 forming the cooling water inlet and outlet 113a, 113b protrude upward from the upper surface 110a. Thus, as illustrated in FIG. 2B, when the male plate 100 is stacked on the female plate 110, the edge parts 107 and 117 are coupled. Further, the upper and lower first flow paths 131 are connected through the cooling water inlet and outlet 103a, 103b and the cooling water inlet and outlet 113a, 113b. Accordingly, in the respective first flow paths 131, the upper and lower first flow paths 131 are connected, and thus all the first flow paths 131 are connected through the cooling water inlet and outlet 103a, 103b and the cooling water inlet and outlet 113a, 113b.

Here, the cooling water inlet and outlet 103a, 103b and the cooling water inlet and outlet 113a, 113b are open to the first flow paths 131, but the oil inlet and outlet 102a, 102b and the oil inlet and outlet 112a, 112b are closed against the first flow paths 131. Further, the oil inlet and outlet 102a, 102b and the oil inlet and outlet 112a, 112b are open to the second flow paths 132, but the cooling water inlet and outlet 103a, 103b and the cooling water inlet and outlet 113a, 113b are closed against the second flow paths 132. Thus, the first flow paths 131 are independent from the second flow paths 132.

The grooves 115 are grooves to disturb the flow of the fluid flowing along the upper surface 110a. The plurality of grooves 115 are provided so as to be recessed downward from a flat part of the upper surface 110a, and each of the grooves 115 extends linearly when viewed from above. The upper surface 110a is divided into two regions 118a and 118b, and the plurality of grooves 115 are provided in each of the regions 118a and 118b.

The regions 118a and 118b are regions obtained by dividing the upper surface 110a. The regions 118a and 118b each have a rectangular shape extending in the front-rear direction. The regions 118a and 118b are obtained by dividing the upper surface 110a substantially symmetrically in the left-right direction. In an embodiment of the present disclosure, the region provided on the left side of the upper surface 110a is the region 118a, and the region provided on the right side is the region 118b.

Here, for the sake of explanation, the grooves 115 provided in the region 118a and the grooves 115 provided in the region 118b will be referred to as grooves 115a and 115b, respectively. The plurality of grooves 115a provided in the region 118a are provided so as to be parallel to each other, and the plurality of grooves 115b provided in the region 118b are also provided so as to be parallel to each other. Further, the grooves 115a extend in the direction intersecting the extending direction of the grooves 115b. Note that the plurality of grooves 115 form a so-called herringbone pattern when viewed from above.

The protrusions 114 are protrusions to disturb the flow of the fluid flowing along the lower surface 110b, and protrude downward from a flat part of the lower surface 110b, and extends linearly when viewed from below. FIG. 9 is a bottom view of the female plate 110. The plurality of protrusions 114 are provided at the lower surface 110b. Since the protrusions 114 and the grooves 115 are formed by press working, the protrusions 114 have the same shape as that of the grooves 115 when viewed in the vertical direction. The protrusions 114 are aligned with the grooves 115 when viewed from below. In other words, the protrusions 114 are provided at the lower surface 110b so as to be paired with the grooves 115 having the same shapes, respectively. The lower surface 110b is divided into two regions 118c and 118d, and the plurality of protrusions 114 are provided in each of the regions 118c and 118d.

The regions 118c and 118d are regions provided by dividing the lower surface 110b. The regions 118c and 118d each have a rectangular shape extending in the front-rear direction. The regions 118c and 118d are obtained by dividing the lower surface 110b substantially symmetrically in the left-right direction. In an embodiment of the present disclosure, the region provided on the right side in the lower surface 110b is the region 118c, and the region provided on the left side is the region 118d. Further, the region provided at the back surface of the region 118a is the region 118c, and the region provided at the back surface of the region 118b is the region 118d.

Here, for the sake of explanation, the protrusions 114 provided in the region 118c and the protrusions 114 provided in the region 118d will be referred to as protrusions 114a and 114b, respectively. The protrusions 114a, 114b are respectively paired with the grooves 115a, 115b having the same shapes, respectively. In other words, the plurality of protrusions 114a provided in the region 118c are provided so as to be parallel to each other, and the plurality of protrusions 114b provided in the region 118d are also provided so as to be parallel to each other. Further, the protrusions 114a extend in the direction intersecting the extending direction of the protrusions 114b. Note that the plurality of protrusions 114 form a so-called herringbone pattern when viewed from below. Further, the protrusions 114 are provided in the direction intersecting the direction of the protrusions 104, when viewed from below, when the male plate 100 and the female plate 110 are stacked.

As illustrated in FIG. 11, the height of the protrusions 114 is about half the height of the space (the first flow path 131) formed when the female plate 110 is stacked on the male plate 100. The protrusions 114 contact the joint parts 101, to thereby join the protrusions 104, so that the joint parts 111 having dot-shaped recesses that are recessed upward from the lower surface of the protrusions 114 are formed. The dot-shaped protrusions of the joint parts 101 are paired with the dot-shaped recesses of the joint parts 111. The joint parts 111 are provided at positions at which the protrusions 104 and the protrusions 114 intersect, when viewed from below, when the female plate 110 is stacked on the male plate 100.

(Fin)

The fin 120 is a member to cause the flows of the fluid running therethrough to be complex and exchange heat with the fluid. The fin 120 is a metal member obtained such that thin plates extending in the front and back and vertical directions, and thin plates extending in the right and left and vertical directions are combined to form a large number of rectangular holes, and has a flat-plate outer shape. The thickness of the fin 120 is substantially the same as the height of the space (the second flow path 132) formed with the male plate 100 and the female plate 110, as illustrated in FIG. 11. The upper surface of the fin 120 contacts the lower surface 100b. The lower surface of the fin 120 contacts the upper surface 110a.

(Top Plate)

The top plate 50 is a member disposed as the uppermost layer member of the heat exchange unit 20. The top plate 50 is a type of the female plate 110, and has a shape similar to the female plate 110 without the oil inlet/outlet 112a, 112b and the cooling water inlet/outlet 113a, 113b. Thus, the top plate 50 will be described, with the constituents thereof that are the same as those in the female plate 110 being given the same reference numerals. The top plate 50 has the upper surface 110a where the linear grooves 115 are formed and the lower surface 110b where the linear protrusions 114 are formed. The top plate 50 is joined, by brazing, to the upper surface of the male plate 100, which is the uppermost member of the stacked section 40. This closes the oil inlet and outlet 102a, 102b of the male plate 100 that is joined to the lower surface of the top plate 50.

An operation of the oil cooler 2 will be described. Inside the oil cooler 2, the cooling water flows through the first flow path 131. The engine oil flows through 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 being placed therebetween. Thus, the cooling water and the engine oil exchange heat through the male plate 100 or the female plate 110. In other words, the high-temperature engine oil is cooled by the low-temperature cooling water. In contrast, the low temperature cooling water is heated by the high temperature engine oil.

(Cooling Water)

As given by the arrows in FIG. 2B, the cooling water is supplied from the cooling water flow path 8 to the cooling water inlet 13a. The cooling water flows from the cooling water inlet 13a into the first flow path 131 in a bottom layer. The cooling water flows into all the first flow paths 131 through the cooling water inlets 103a, 113a.

The cooling water spreads and flows throughout the first flow paths 131 from the cooling water inlets 103a, 113a, as given by the arrows in FIG. 12. The cooling water then flows into the cooling water outlets 103b, 113b.

A portion of the cooling water that has flown in, contacts the protrusions 104, 114 while flowing through the first flow path 131. Since the protrusions 104, 114 protrude vertically, the cooling water that contacts the protrusions 104, 114 generates a flow in the vertical direction. Further, since the protrusions 104, 114 are provided to intersect the flow direction of the cooling water, the cooling water that contacts the protrusions 104, 114 generates flows in the left-right direction according to the angle at which they intersect. Further, with the protrusions 104, 114 contacting at the joint parts 101, 111, the protrusions 104, 114 at those positions form columnar shapes. Accordingly, a portion of the cooling water generates flows avoiding the protrusions 104, 114 formed into columnar shapes. As such, the cooling water generates complex flows when flowing through the first flow path 131.

When flowing through the first flow paths 131, the cooling water exchanges heat with the engine oil through the male plate 100 and the female plate 110. The surface area of the male plate 100 increases by an amount corresponding to the provided projections 104. Further, the surface area of the female plate 110 increases by an amount corresponding to the provision of the protrusions 114. Here, the more the contact area between the cooling water and the member that exchanges heat increases, the more the efficiency of the heat exchange by the cooling water increases. Thus, the efficiency of the heat exchange by the cooling water flowing through the first flow paths 131 is high.

The cooling water flows through each of the first flow paths 131 and flows into the cooling water outlets 103b, 113b. The cooling water flows into the cooling water outlet 13b through the cooling water outlets 103b and 113b. The cooling water flows into the radiator 5 through the cooling water flow path 8 from the cooling water outlet 13b.

(Engine Oil)

As given by the arrows in FIG. 2B, the engine oil is supplied from the oil flow path 7 to the oil inlet 12a. The engine oil flows from the oil inlet 12a into the second flow path 132 at the bottom layer. The engine oil flows into all the second flow paths 132 through the oil inlets 102a and 112a.

The engine oil spreads and flows throughout the second flow paths 132 from the oil inlets 102a, 112a, as given by the arrows in FIG. 13. The engine oil then flows into the oil outlets 102b, 112b.

The engine oil that has flown in, contacts the fin 120 while flowing through the second flow path 132. Further, the engine oil flows through the holes formed in the fin 120 and through the grooves 105, 115. The engine oil flowing through the second flow path 132 contacts the fin 120, and flows through the grooves 105, 115, thereby generating flows in the left-right direction and the up-down direction.

The engine oil exchanges heat with the cooling water through the male plate 100, the female plate 110, and the fin 120, while flowing through the second flow path 132. Since the fin 120 contacts the lower surface 100b and the upper surface 110a, heat is exchanged between the fin 120 and the male plate 100 and between the fin 120 and the female plate 110. In other words, the fin 120 increases the area for the engine oil to exchange heat. Further, the surface area of the male plate 100 increases by an amount corresponding to the provided grooves 105. Similarly, the surface area of the female plate 110 increases by an amount corresponding to the provided grooves 115. Thus, the efficiency of the heat exchange by the engine oil flowing through the second flow paths 132 is high.

The engine oil runs through the fin 120 while flowing through the second flow path 132. The fin 120 makes it difficult for the engine oil to flow in the second flow path 132. As a result, the pressure loss in the second flow path 132 increases. However, the upper/lower surfaces of the fin 120 contact the grooves 105, 115. Since the size of the grooves 105, 115 is larger than the size of the flow paths inside the fin 120, a portion of the engine oil running through the fin 120 flows from the inside of the fin 120 to the grooves 105, 115.

The engine oil flows through the respective second flow paths 132 into the oil outlets 102b, 112b. The engine oil flows into the oil outlet 12b through the oil outlets 102b, 112b. The engine oil flows into the oil pump 4 through the oil flow path 7 from the oil outlet 12b.

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

With the protrusions 104, 114 configured to contact the cooling water being formed at the plate, the contact area between the cooling water and the plate increases. The more the contact area of the plate that contacts the cooling water during heat exchange increases, the more the efficiency of the heat exchange by the cooling water increases, and thus the efficiency of the heat exchange by the oil cooler 2 increases.

Further, with the cooling water contacting the protrusions 104, the flow of the cooling water changes along the projections 104. Accordingly, the flows of the cooling water become complex. The more the complex flows of the cooling water are generated, the more the efficiency of the heat exchange by the cooling water increases, and thus the efficiency of the heat exchange by the oil cooler 2 increases.

Further, the plurality of protrusions 104, 114 of the oil cooler 2 according to an embodiment of present disclosure each extend to intersect the flow direction of the cooling water.

The plurality of protrusions 104, 114 extending in the direction intersecting the flow direction of the cooling water, generates a flow of the cooling water according to the angle at which the flow direction of the cooling water intersects the protrusions 104, 114 when the cooling water contacts the protrusions 104, 114. Accordingly, the cooling water generates complex flows, thereby increasing the efficiency of the heat exchange.

Further, the upper surface 100a or the lower surface 110b of the oil cooler 2 according to an embodiment of the present disclosure is divided into the region 108a and the region 108b, or the region 118c and the region 118d, each extending in the flow direction of the cooling water, and in the plurality of protrusions 104, 114, the protrusions 104a in the region 108a and the protrusions 104b in the region 108b extend in directions intersecting each other, or the protrusions 114a in the region 118c and the protrusions 114b in the region 118d extend in directions intersecting each other.

The upper surface 100a or the lower surface 110b is divided into the region 108a and the region 108b, or the region 118c and the region 118d, each extending in the flow direction of the cooling water, and in the protrusions 104, 114, the protrusions 104a in the region 108a and the protrusions 104b in the region 108b extend in directions intersecting each other, or the protrusions 114a in the region 118c and the protrusions 114d in the region 118d extend in directions intersecting each other. This causes the flow direction of the cooling water in the region 108a to be different from the flow direction of the cooling water in the region 108b. Alternatively, the flow direction of the cooling water in the region 118c is caused to be different from the flow direction of the cooling water in the region 118d. Accordingly, the cooling water generates complex flows, thereby increasing the efficiency of the heat exchange.

Further, the plate of the oil cooler 2 according to an embodiment of the present disclosure further includes the lower surface 100b located on the side opposite to the upper surface 100a or the upper surface 110a located on the side opposite to the lower surface 110b, which are to be contacted by the engine oil that exchanges heat with the cooling water. The plurality of linearly extending grooves 105, 115 are formed at the lower surface 100b or the upper surface 110a.

The plate includes the lower surface 100b located on the side opposite to the upper surface 100a or the upper surface 110a located on the side opposite to the lower surface 110b, which are to be contacted by the engine oil that exchanges heat with the cooling water. With the plurality of linearly extending grooves 105, 115 being formed at the lower surface 100b or the upper surface 110a, the lower surface 100b or the upper surface 110a results in a wavy shape. Accordingly, the contact area between the engine oil and the plate increases. The more the contact area between the engine oil and the member to contact the oil during heat exchange increases, the more the efficiency of the heat exchange by the engine oil increases, thereby increasing the efficiency of the heat exchange by the oil cooler 2.

Further, with the lower surface 100b or the upper surface 110a being in a wavy shape, the engine oil flows along the grooves 105, 115. As a result, the engine oil generates complex flows, thereby increasing the efficiency of the heat exchange.

Furthermore, the cooling water and the engine oil exchange heat through the plates. Not only the efficiency of the heat exchange between the upper surface 100a or the lower surface 110b and the cooling water, but also the efficiency of the heat exchange between the lower surface 100b or the upper surface 110a and the engine oil increases, and thus the efficiency of the heat exchange of the entire oil cooler 2 increases.

Further, the plurality of grooves 105, 115 of the oil cooler 2 according to an embodiment of the present disclosure each extend to intersect the flow direction of the engine oil.

With the plurality of grooves 105, 115 each extending in the direction intersecting the flow direction of the engine oil, a flow of the engine oil is generated according to the angle at which the direction of the flow of the engine oil intersects the grooves 105, 115, when the engine oil flows along the grooves 105, 115. Accordingly, the engine oil generates complex flows, thereby increasing the efficiency of heat exchange.

Further, the lower surface 100b or the upper surface 110a of the oil cooler 2 according to an embodiment of the present disclosure is divided into the region 108c and the region 108d, or the region 118a and the region 118b, each extending in the flow direction of the engine oil, and in the plurality of grooves 105, 115, the grooves 105a in the region 108c and the grooves 105b in the region 108d extend in directions intersecting each other, or the grooves 115a in the region 118a and the grooves 115b in the region 118b extend in directions intersecting each other.

The lower surface 100b or the upper surface 110a is divided into the region 108c and the region 108d, or the region 118a and the region 118b, each extending in the flow direction of the engine oil, and in the grooves 105, 115, the grooves 105a in the region 108c and the grooves 105b in the region 108d extend in directions intersecting each other, or the grooves 115a in the region 118a and the grooves 115b in the region 118b extend in directions intersecting each other, thereby causing the flow direction of the engine oil in the region 108c to be different from the flow direction of the engine oil in the region 108d. Alternatively, the flow direction of the engine oil into the region 118a is caused to be different from the flow direction of the engine oil into the region 118b. Accordingly, the engine oil generates complex flows, thereby increasing the efficiency of heat exchange.

Further, the oil cooler 2 according to an embodiment of the present disclosure further includes the fin 120 configured to diffuse the flow of the cooling water or engine oil that contacts either at least one of the plurality of protrusions 104 or the lower surface 100b, or contacts either at least one of the plurality of protrusions 114 or the upper surface 110a.

The flow of the cooling water or engine oil is diffused by the fin 120 configured to diffuse the flow of the cooling water or engine oil that contacts either at least one of the plurality of protrusions 104 or the lower surface 100b, or either at least one of the plurality of protrusions 114 or the upper surface 110a. Accordingly, the part where the cooling water or engine oil contacts the plates increases, thereby increasing the amount of heat exchange between the cooling water or engine oil and the plates. As a result, the efficiency of the heat exchange of the entire oil cooler 2 increases.

Further, the fins 120 contact either the protrusions 104 or the lower surface 100b, or either the protrusions 114 or the upper surface 110a, and thus the fins 120 contacts the plates. Accordingly, the members that exchange heat with the cooling water or engine oil increase. As a result, the efficiency of the heat exchange of the entire oil cooler 2 increases.

Note that the fin 120 increases the efficiency of the heat exchange as described above. Meanwhile, the fin 120 increases resistance in the flow path of the cooling water or engine oil, which increases the pressure loss in the flow path. Here, the fin 120 contacts either the protrusion(s) 104 or the lower surface 100b, and thus the fin 120 contacts, at the contact part, the grooves formed between the plurality of protrusions 104 or the grooves 105 formed at the lower surface 100b. Alternatively, the fin 120 contacts either the protrusion(s) 114 or the upper surface 110a, and thus the fin 120 contacts, at the contact part, the grooves formed between the plurality of protrusions 114 or the grooves 115 formed at the upper surface 110a. Since these grooves function as the flow path for the cooling water or engine oil, the pressure loss in the flow path decreases. In other words, it is possible to achieve the effects of increasing the efficiency of the heat exchange by the fin 120 while suppressing the increase in the pressure loss in the flow path.

Further, the plurality of protrusions 104, 114 of the oil cooler 2 according to an embodiment of the present disclosure are aligned with the plurality of grooves 105, 115 when viewed in the direction orthogonal to the upper surface 100a or the lower surface 110b.

The plurality of protrusions 104, 114 are aligned with the plurality of grooves 105, 115 when viewed in the direction orthogonal to the upper surface 100a or the lower surface 110b, so that the protrusions 104 and the grooves 105, or the protrusions 114 and the grooves 115 are respectively located at the same positions at the front and back surfaces of the plate. Here, in order to provide the grooves 105, 115 at the lower surface 100b or the upper surface 110a, the thickness of the plate needs to be thicker than the depth of the grooves 105, 115. However, if the protrusions 104 and the grooves 105 or the protrusions 114 and the grooves 115 are respectively located at the same positions at the front and back surfaces of the plate, the grooves 105 can be provided from the lower surface 100b with respect to the protruding parts of the corresponding protrusions 104, or the grooves 115 can be formed from the upper surface 110a with respect to the protruding parts of the corresponding protrusions 114, which makes it possible to make the plate thinner. This results in achieving the thinner oil cooler 2.

Further, the oil cooler 2 according to an embodiment of the present disclosure further includes the plate having the lower surface 110b or the upper surface 100a configured to contact the cooling water, the lower surface 110b or the upper surface 100a having the plurality of protrusions 114, 104 extending linearly formed thereat, and the upper surface 100a faces the lower surface 110b.

The oil cooler 2 includes the plate having the lower surface 110b or the upper surface 100a configured to contact the cooling water, the lower surface 110b or the upper surface 100a having the plurality of protrusions 114, 104 extending linearly formed thereat. Here, with the upper surface 100a and the lower surface 110b facing each other, the cooling water flows between the upper surface 100a and the lower surface 110b. Accordingly, the cooling water contacts not only the protrusions 104 but also the protrusions 114, and thus the cooling water generates more complex flows. As a result, the efficiency of the heat exchange increases.

Further, at least one of the plurality of protrusions 104 of the oil cooler 2 according to an embodiment of the present disclosure contacts corresponding one of the plurality of protrusions 114.

With at least one of the plurality of protrusions 104 contacting corresponding one of the plurality of protrusions 114, the contact portions of such two protrusions form a column or a wall between the upper surface 100a and the lower surface 110b. Accordingly, the cooling water flows in such a manner as to avoid the column or wall, and thus the cooling water generate more complex flows. As a result, the efficiency of the heat exchange increases.

Further, since such columns or walls are formed between the plates, the oil cooler 2 has high strength against the force acting in the direction in which the plates face each other.

Further, each of the plurality of protrusions 104 of the oil cooler 2 according to an embodiment of the present disclosure extends in a direction intersecting the plurality of protrusions 114.

Each of the plurality of protrusions 104 extends in the direction intersecting the plurality of protrusions 114, and thus the direction of the wavy shape formed at the upper surface 100a is different from the direction of the wavy shape formed at the lower surface 110b. Accordingly, the cooling water generates complex flows, while flowing between the upper surface 100a and the lower surface 110b. As a result, the efficiency of the heat exchange increases.

Variations described below may be applied in combination.

(1) Modification 1

Immediately after the heat exchange system 1 starts operating, and the like, the temperature of the engine oil may be lower than the temperature of the cooling water. In this case, the oil cooler 2 exchanges heat between the low-temperature engine oil and the high-temperature water. As a result, the engine oil is heated while the water is cooled.

(2) Modification 2

The configuration 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 locations. Further, the engine 3 may be replaced with a transmission or a motor. In this case, the engine oil is replaced with a transmission oil or a motor oil.

(3) Modification 3

The fluid that exchanges heat with the water may be a gas. For example, the oil cooler 2 functions as an EGR cooler of an Exhaust Gas Recirculation (EGR) system that recirculates the exhaust gas from the engine 3, to mix it with the intake gas of the engine 3. The EGR cooler takes in a portion of the exhaust gas discharged from the engine 3, exchanges heat between the exhaust gas and the water, to thereby cool the exhaust gas. Then, the exhaust gas cooled by the EGR cooler is mixed with the intake gas of the engine 3. In this case, in the heat exchange system 1, the oil pump 4 is removed and the oil flow path 7 results in a gas flow path.

(4) Modification 4

The flow directions of the engine oil and the cooling water may be different. In other words, in an embodiment of the present disclosure, the engine oil flows from the oil flow path 7 in the order of the oil inlet 12a, the oil inlet 112a, the second flow path 132, the oil outlet 112b, and the oil outlet 12b. However, the oil may flow from the oil flow path 7 in the order of the oil outlet 12b, the oil outlet 112b, the second flow path 132, the oil inlet 112a, and the oil inlet 12a. Similarly, the cooling water may flow from the cooling water flow path 8 in the order of the cooling water outlet 13b, the cooling water outlet 103b, the first flow path 131, the cooling water inlet 103a, and the cooling water inlet 13a.

(5) Modification 5

Each of the plurality of protrusions 104, 114 does not have to extend in the direction intersecting the flow direction of the cooling water. In this case, at least one of the plurality of protrusions 104, 114 extends parallel to the flow direction of the cooling water.

(6) Modification 6

The upper surface 100a or the lower surface 110b does not have to be divided into the region 108a and the region 108b, or the region 118c and the region 118d, each extending in the flow direction of the cooling water, and in the plurality of protrusions 104 or 114, the protrusions 104a in the region 108a and the protrusion 104b in the region 108b, or the protrusions 114a in the region 118c and the protrusions 114b in the region 118d, do not have to extend in directions intersecting each other. In this case, the upper surface 100a or the lower surface 110b is not divided into two regions. Further, at the upper surface 100a or the lower surface 110b, the plurality of projections 104 or projections 114 may extend in parallel to each other, or may extend in directions intersecting each other.

(7) Modification 7

The plate does not need to have the plurality of linearly extending grooves 105 or 115 formed at the lower surface 100b or the upper surface 110a. In this case, the lower surface 100b or the upper surface 110a may be a flat surface. Further, the lower surface 100b or the upper surface 110a may be embossed or provided with protrusions or bosses.

(8) Modification 8

Each of the plurality of grooves 105, 115 does not have to extend to intersect the flow direction of the engine oil. In this case, at least one of the plurality of grooves 105, 115 extends parallel to the flow direction of the engine oil.

(9) Modification 9

The lower surface 100b or the upper surface 110a does not have to be divided into the region 108c and the region 108d, or the region 118a and the region 118b, each extending in the flow direction of the engine oil. In the plurality of grooves 105 or grooves 115, 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, do not have to extend in directions intersecting each other. In this case, the lower surface 100b or the upper surface 110a is not divided into two regions. Further, at the lower surface 100b or the upper surface 110a, the plurality of grooves 105 or grooves 115 may extend in parallel to each other, or may extend in directions intersecting each other.

(10) Modification 10

The oil cooler 2 does not have to include the fin 120 that contacts the lower surface 100b or the upper surface 110a. In this case, the fin 120 is not provided at the second flow path 132.

(11) Modification 11

The oil cooler 2 may include the fin 120 that contacts the protrusions 104, 114. In this case, for example, the heights of the protrusions 104, 114 and the heights of the fin 120 are changed, such that the fin 120 is provided at the first flow path 131 so as to contact the protrusions 104, 114.

(12) Modification 12

The plurality of protrusions 104, 114 do not have to be aligned with the plurality of grooves 105, 115 when viewed in the direction orthogonal to the upper surface 100a or the lower surface 110b. In this case, the plurality of protrusions 104, 114 are deviated from the plurality of grooves 105, 115 when viewed in the direction orthogonal to the upper surface 100a or the lower surface 110b, and thus the thickness of the plate increases by an amount corresponding to the depth of the grooves 105, 115.

(13) Modification 13

The oil cooler 2 may include only either the male plate 100 or the female plate 110. For example, the stacked section 40 can be configured such that the male plates 100 and plates other than the female plate 110 are alternately stacked in the vertical direction, or the female plates 110 and plates other than the male plate 100 are alternately stacked in the vertical direction.

(14) Modification 14

The plurality of protrusions 104, 114 do not have to contact the plurality of protrusions 114, 104. In this case, for example, the heights of the plurality of protrusions 104 and 114 are lower than half of the heights of the first flow path 131 and the second flow path 132.

(15) Modification 15

The plurality of protrusions 104, 114 do not have to extend in the directions intersecting the plurality of protrusions 114, 104, respectively. In this case, at least one of the plurality of protrusions 104, 114 extends parallel to the plurality of protrusions 114, 104.

(16) Modification 16

The plurality of protrusions 104, 114 and the plurality of grooves 105, 115 do not have to be linear. The lines formed by the plurality of protrusions 104, 114 and the plurality of grooves 105, 115 include not only straight lines but also curved lines and broken lines. Thus, the plurality of protrusions 104, 114 and the plurality of grooves 105, 115 may have a curved-line shape or broken-line shape. The broken line shape includes, for example, a V-shape, an inverted V-shape, an X-shape, and the like, and also includes a combination of these shapes.

(17) Modification 17

The plurality of protrusions 104, 114 and grooves 105, 115 may include a plurality of line types. In this case, for example, the plurality of protrusions 104, 114 and the plurality of grooves 105, 115 include those having a linear shape and a curved shape within one plate.

(18) Modification 18

In an embodiment of the present disclosure, the engine oil and the cooling water flow into or out of the oil cooler 2 through the oil inlets/outlets 12a, 12b and the cooling water inlets/outlets 13a, 13b, but other structures may be used. For example, as illustrated in FIG. 14, the top plate 50 may be have oil inlet/outlet 52a, 52b and cooling water inlet/outlet 53a, 53b. The oil inlet/outlet 52a, 52b and the cooling water inlet/outlet 53a, 53b are tubular members attached to openings provided at the four corners of the top plate 50, and the member attached at the rear right when viewed from above is the oil inlet 52a. The member attached to the front left is the oil outlet 52b, the member attached to the rear left is the cooling water inlet 53a, and the member attached to the front right is the cooling water outlet 53b. The oil inlet and outlet 52a, 52b are connected to the oil flow path 7 to form an engine oil flow path. Similarly, the cooling water inlet and outlet 53a, 53b are connected to the cooling water flow path 8 to form a cooling water flow path.

(19) Modification 19

In an embodiment of the present disclosure, the plurality of protrusions 104, 114 and the grooves 105, 115 are provided in the rectangular regions 108a, 108b, 108c, 108d, 118a, 118b, 118c, and 118d, but may be provided in the upper surfaces 100a, 110a and the lower surfaces 100b, 110b other than the above. For example, it is assumed that in the male plate 100, the sizes of the oil inlet and outlet 102a, 102b and the cooling water inlet and outlet 103a, 103b are reduced only in the left-right direction, and are arranged at the end portions of the male plate 100 in the left-right direction. In this case, at the upper surface 100a and the lower surface 100b, a flat part is formed between the oil inlet 102a and the cooling water inlet 103a and between the oil outlet 102b and the cooling water outlet 103b. The protrusions 104 and the grooves 105 are provided at these flat parts.

(20) Modification 20

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

(21) Modification 21

In an embodiment of the present disclosure, the size of the angle formed by the protrusions 104a and 104b intersecting with the center line extending in the front-rear direction when viewed from above is the same as the size of the angle formed by the protrusions 114a and 114b intersecting with the center line extending in the front-rear direction when viewed from above, but may be different therefrom. For example, the angle formed by the protrusions 104a and 104b intersecting with the center line that is a straight line extending in the front-rear direction when viewed from above is set to 30 degrees, and the angle formed by the protrusions 114a, 114b intersecting with the center line that is a straight line extending in the front-rear direction when viewed from above is 120 degrees.

REFERENCE SIGNS LIST

- 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 groove
- 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 fin (diffusion member)

HEAT EXCHANGER

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