JP2017044461A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger using a metal porous body which can improve an efficient heat exchange.SOLUTION: A heat sink 100 comprises: a heat transfer part 12; a fluid passage part 20 which is composed of a metal porous body, is disposed in contact with the heat transfer part 12, and allows a cooling water 1 to pass through therein; and a flow guiding path part 81 for defining a flow guiding path 82 which guides the cooling water 1 into the fluid passage part 20. An area of a flow-in face 25 of the fluid passage part 20 in which the cooling water 1 flows in is made larger than an area of a cross-section 72b of the flow guiding path, which is a cross-section of the flow guiding path 82 vertical to a flow direction 1a of the cooling water 1, positioned in a region adjacent to an upstream side of a flow-in position 70 which is a position in contact with the fluid passage part 20 when the cross-section 72a is moved closer to the fluid passage part 20 along the flow direction of the cooing water 1.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a heat exchanger.

  Improvement of the efficiency of heat exchange in the heat exchanger is an important factor that leads to downsizing of the heat exchanger and energy saving of the system including the heat exchanger.

  As a technique for improving the efficiency of heat exchange in a heat exchanger, a technique for improving heat transfer performance by using a foam metal produced by foaming a metal material on a fin of a heat exchanger is disclosed (for example, , See Patent Document 1). Patent Document 1 discloses that the efficiency of heat exchange is improved by adopting a metal foam made of copper, aluminum, or the like having high thermal conductivity as a heat transfer fin of a heat exchanger for an air conditioner. .

JP 2005-326136 A

  In patent document 1, it is supposed that the efficiency of a heat exchanger will improve by making the eyes of a metal foam fine. However, when the metal foam is made finer, the pressure resistance for flowing the fluid to the heat exchanger increases, so when flowing the fluid under the same pressure as the conventional heat exchanger, There is a possibility that the flow rate of the fluid decreases and the efficiency of the heat exchanger decreases.

  Therefore, an object of the present invention is to provide a heat exchanger that can improve the efficiency of heat exchange while suppressing an increase in pressure resistance in a heat exchanger using a metal porous body.

  The heat exchanger according to the present invention is composed of a heat transfer section and a porous metal body, is disposed in contact with the heat transfer section, allows a fluid to pass through the inside, and allows the fluid to pass to the fluid passage section. An introduction flow path section for defining an introduction flow path to be led. The area of the inflow surface, which is the surface through which the fluid flows in the fluid passage portion, is such that the introduction passage section, which is a section of the introduction passage perpendicular to the fluid traveling direction, is brought closer to the fluid passage portion along the fluid traveling direction. In this case, it is larger than the area of the cross section of the introduction channel located in the region adjacent to the upstream side of the inflow position, which is the position in contact with the fluid passage portion.

  According to the heat exchanger, in the heat exchanger using the metal porous body, it is possible to improve the efficiency of heat exchange while suppressing an increase in pressure resistance.

It is a schematic perspective view which shows an example of the structure of a heat exchanger. It is AA sectional drawing of FIG. It is BB sectional drawing of FIG. It is a schematic sectional drawing which shows another example of the structure of a heat exchanger. It is a schematic sectional drawing which shows another example of the structure of a heat exchanger. It is a schematic perspective view which shows another example of the structure of a heat exchanger. It is CC sectional drawing of FIG. It is a figure which shows the relationship between a pressure loss and thermal resistance. It is a figure which shows the temperature distribution in a fluid passage part.

[Description of Embodiment of Present Invention]
First, embodiments of the present invention will be listed and described. The heat exchanger of the present application is composed of a heat transfer section and a metal porous body, and is disposed in contact with the heat transfer section, and a fluid passage section through which a fluid can pass, and the fluid to the fluid passage section. An introduction flow path section for defining an introduction flow path to be led. The area of the inflow surface, which is the surface into which the fluid flows in the fluid passage portion, is the same as the cross section of the introduction flow channel that is perpendicular to the direction of movement of the fluid. And larger than the area of the cross section of the introduction flow channel located in the region adjacent to the upstream side of the inflow position, which is a position in contact with the fluid passage portion when approaching the fluid passage portion.

  When a metal porous body is disposed in a fluid flow path that is a heat exchange medium of the heat exchanger, the heat transfer efficiency between the fluid and the metal porous body is increased by making the metal porous body finer. On the other hand, when the metal porous body is made finer, the resistance when the fluid passes through the metal porous body is increased, and the pressure loss is increased. Therefore, when a fluid is flowed under the same pressure as a conventional heat exchanger, the flow rate of the fluid flowing into the heat exchanger is reduced, and the efficiency of the heat exchanger may be reduced. As a result, there arises a problem that it is difficult to improve the efficiency of heat exchange in the heat exchanger.

  The present inventors examined a structure capable of improving the efficiency of heat exchange in a heat exchanger using a metal porous body. As a result, it has been found that the heat exchange efficiency can be improved by adopting the structure of the heat exchanger. If it demonstrates in detail, the heat exchanger of this application consists of a metal porous body, is arrange | positioned in contact with a heat-transfer part, and is provided with the fluid passage part which can let a fluid pass through the inside. When the introduction channel cross section, which is a section of the introduction channel perpendicular to the fluid traveling direction, is brought close to the fluid passage portion along the fluid traveling direction, the fluid flows to the fluid passage portion. The area of the inflow surface is larger than the area of the cross section of the introduction flow channel located in a region adjacent to the upstream side of the inflow position, which is a position in contact with the fluid passage portion. By doing so, the velocity of the fluid decreases before the fluid flows into the fluid passage portion. Here, the pressure loss is proportional to the square of the fluid velocity. In particular, in a low-viscosity fluid generally used in a heat exchanger such as air or water, the pressure loss is proportional to the square of the fluid velocity. The pressure loss is also proportional to the fluid permeation length. For this reason, when the cross-sectional area of the flow path is multiplied by K while the volume of the metal porous body is constant, the liquid permeation distance is 1 / K times and the fluid velocity is also 1 / K times. It is inversely proportional to the cube of the area. The amount of heat exchange is proportional to the 0th power to the 1st power of the inflow speed of the metal porous body into the fluid passage portion. In particular, when the fluid is air or water, the heat exchange amount is proportional to the inflow speed to the power of 0.6. For this reason, when the cross-sectional area of the flow path is increased by K times, the heat exchange amount decreases in inverse proportion to K to the power of 0.6. Summarizing these relationships, it can be seen that the amount of heat exchange is small with respect to a significant decrease in pressure loss. For this reason, when it sees with the same pressure loss, if K is enlarged enough, the amount of heat exchange will increase. Thus, according to the heat exchanger of this application, in the heat exchanger using a metal porous body, it becomes possible to improve the efficiency of heat exchange.

  The heat exchanger may further include a heat conduction auxiliary member that is disposed so as to connect the region of the fluid passage portion located away from the heat transfer portion and the heat transfer portion. Thereby, in the said fluid passage part, the movement of the heat | fever between the area | region away from the contact surface of the said heat-transfer part and a heat-transfer part becomes easy. As a result, the efficiency of heat exchange can be further improved.

  In the heat exchanger, the heat transfer section may define a passage channel through which the fluid passes through the fluid passage section by surrounding the fluid passage section. Thereby, a heat exchanger with a simple structure can be obtained.

  In the heat exchanger, the area of the inlet channel is larger than the area of the inlet channel cross section located in a region adjacent to the upstream side of the inlet position at the inlet position. The area of the cross section of the introduction flow channel located in a region adjacent to the upstream side of the inflow position may be larger. By doing in this way, the inflow speed of the fluid to a fluid passage part can be reduced easily. In particular, a high-performance heat exchanger can be obtained when the area of the cross section of the introduction flow path at the inflow position exceeds 18 times the area of the cross section of the introduction flow path located upstream of the inflow position. .

  In the heat exchanger, when the inflow surface is inclined with respect to a cross section of the introduction flow path at the inflow position, the area of the inflow surface is located in a region adjacent to the upstream side of the inflow position. It may be larger than the area of the road cross section. By doing in this way, the area of the said inflow surface can be enlarged and the inflow speed of the fluid to a fluid passage part can be reduced, suppressing that the size of a heat exchanger becomes large.

  In the heat exchanger, an upstream concave portion having an opening on the upstream side and having a bottom wall inside is formed in the fluid passage portion, so that the area of the inflow surface is adjacent to the upstream side of the inflow position. It may be larger than the area of the introduction channel cross section located in the region. By doing in this way, the area of the said inflow surface can be enlarged and the inflow speed of the fluid to a fluid passage part can be reduced.

  In the heat exchanger, a downstream recess having an opening on the downstream side and having a bottom wall inside the fluid passage may be formed apart from the upstream recess. By doing so, the fluid that has flowed into the upstream recess is allowed to pass through the fluid passage located between the upstream recess and the downstream recess, and then discharged from the downstream recess. This path can be easily formed.

[Details of the embodiment of the present invention]
(Embodiment 1)
Next, Embodiment 1 which is one embodiment of the heat exchanger according to the present invention will be described below with reference to the drawings. In the following drawings, the same or corresponding parts are denoted by the same reference numerals, and description thereof will not be repeated.

  Referring to FIG. 1, heat sink 100, which is a heat exchanger according to the first embodiment, can flow a fluid such as cooling water, which is a heat exchange medium, inside a heat transfer body that is in contact with a heat source, for example. It has a structure.

  Referring to FIGS. 1 to 3, heat sink 100 that is a heat exchanger in the present embodiment includes a main body portion 10, a fluid passage portion 20, an introduction pipe 22, and a discharge pipe 28.

  Referring to FIGS. 2 and 3, main body portion 10 is located in the center along heat transfer portion 12 in the direction along traveling direction 1 a of cooling water 1 and on the upstream side as viewed from heat transfer portion 12. It includes an introduction part 23 and a discharge part 34 located on the downstream side when viewed from the heat transfer part 12. The main body 10 is made of a metal having high thermal conductivity such as copper. Moreover, the external shape of the main-body part 10 is a rectangular parallelepiped shape. The main body 10 contacts a heat source (not shown) on the outer wall. The introduction part 23 defines a main body introduction flow path 15 that becomes a flow path of the cooling water 1 introduced into the fluid passage part 20. Further, the discharge part 34 defines the main body discharge flow path 16 that becomes the flow path of the cooling water 1 discharged from the fluid passage part 20.

  The introduction pipe 22 is connected to the introduction part 23 of the main body part 10. The introduction pipe 22 and the introduction part 23 constitute an introduction flow path part 81. The discharge pipe 28 is connected to the discharge part 34 of the main body part 10. An introduction pipe flow path 27 that is a hollow region is formed inside the introduction pipe 22.

  A hollow region 19 that is a through hole is formed in the main body 10. The cross-sectional area in the cross section perpendicular to the traveling direction 1a of the cooling water 1 in the hollow region 19 of the main body 10 is greater than that of the central portion 17 as compared with the main body introduction flow path 15 on the upstream side and the main body discharge flow path 16 on the downstream side. Is getting bigger. The cross-sectional area in the cross section perpendicular to the traveling direction 1 a of the cooling water 1 is constant at the central portion 17. The center part 17 has a rectangular parallelepiped shape. The main body introduction flow path 15 and the main body discharge flow path 16 are surrounded by a smooth curved surface in which a quadrangular pyramid-shaped region connected to the central portion 17 on the bottom surface is curved so that a cross-sectional area decreases as the distance from the region decreases. It has a shape connected to a cylindrical region by the region. The main body introduction flow path 15 and the introduction pipe flow path 27 constitute an introduction flow path 82.

  A fluid passage portion 20 is disposed in the central portion 17 of the hollow region 19. The fluid passage part 20 is disposed so as to contact the heat transfer part 12 of the main body part 10. More specifically, the fluid passage part 20 contacts over the entire circumference of the inner wall surface of the heat transfer part 12. The central portion 17 is filled with the fluid passage portion 20. The heat transfer unit 12 defines a passage channel (central portion 17) for allowing the cooling water 1 to pass through the fluid passage unit 20 by surrounding the fluid passage unit 20.

  The fluid passage part 20 is fixed by brazing to the inner wall surface of the heat transfer part 12, for example. Thereby, the movement of the heat between the fluid passage part 20 and the heat transfer part 12 becomes easy. The fluid passage portion 20 includes an inflow surface 25 that is a surface into which the cooling water 1 should flow. The fluid passage part 20 consists of a metal porous body comprised from a metal with high heat conductivity. The fluid passage part 20 has a porous structure through which the cooling water 1 can pass. Here, the metal porous body may be a foam metal produced by foaming a metal, or may be a porous state produced by another production method. For example, Ni (nickel), Cu (copper), Al (aluminum), Ti (titanium), Fe (iron), or the like can be used as the metal material constituting the metal porous body.

  When the heat sink 100 is in use, the main body 10 contacts a heat source (not shown). Therefore, heat is transmitted from the heat generation source to the main body 10. The heat flowing into the main body portion 10 moves to the fluid passage portion 20 joined to the main body portion 10. The cooling water 1 introduced from the introduction pipe 22 flows into the fluid passage part 20 from the inflow surface 25 and takes heat away from the fluid passage part 20 when passing through the fluid passage part 20. Then, the cooled cooling water 1 is discharged from the discharge pipe 28. In this way, the heat sink 100 releases heat from the heat source.

  Here, the heat sink 100 is composed of a heat transfer section 12 and a metal porous body, is disposed in contact with the heat transfer section 12, and is provided to the fluid passage section 20 through which the cooling water 1 can pass and the fluid passage section 20. And an introduction channel portion 81 that defines an introduction channel 82 that guides the cooling water 1.

  2 and 3, the area of the inflow surface 25 of the fluid passage portion 20 cools the introduction passage section 72 a that is a section of the introduction passage 82 perpendicular to the traveling direction 1 a of the cooling water 1. More than the area of the introduction channel cross section 72b located in the region adjacent to the upstream side of the inflow position 70, which is a position that contacts the fluid passage 20 when approaching the fluid passage 20 along the traveling direction 1a of the water 1. large.

  More specifically, in the present embodiment, the area of the introduction channel cross section at the inflow position 70 is larger than the area of the introduction channel cross section 72b located in the region adjacent to the upstream side of the inflow position 70. The area of the inflow surface 25 is larger than the area of the introduction flow path cross section 72 b located in the region adjacent to the upstream side of the inflow position 70. That is, the cross-sectional area of the flow path of the cooling water 1 is increased before flowing into the inflow surface 25. By having such a structure, in the heat sink 100 of the present embodiment, the speed of the cooling water 1 decreases before the cooling water 1 flows into the fluid passage portion 20. The pressure loss is proportional to the square of the speed of the fluid (cooling water 1). Therefore, it is possible to reduce the pressure loss by reducing the speed of the cooling water 1 flowing into the fluid passage portion 20 made of a metal porous body. As a result, the efficiency of heat exchange can be improved. Thus, according to the heat sink 100 in the present embodiment, in the heat sink 100 using the metal porous body, it is possible to reduce the pressure loss and improve the efficiency of heat exchange.

(Embodiment 2)
Next, a second embodiment which is another embodiment will be described. Referring to FIG. 4, heat sink 200 that is a heat exchanger in the second embodiment is similar to the first embodiment in that main body 30, fluid passage 40, introduction pipe 47, and discharge It is provided with a pipe 48 and is used in the same manner to release heat from the heat source.

  In the direction along the traveling direction 1 a of the cooling water 1, the main body portion 30 includes a heat transfer portion 33 located in the center, an introduction portion 35 located upstream from the heat transfer portion 33, and the heat transfer portion 33. And a discharge portion 36 located on the downstream side as viewed. The main body 30 is made of a metal having high thermal conductivity such as copper. The main body 30 contacts a heat source (not shown) on the outer wall. The introduction part 35 defines a main body introduction flow path 85 that becomes a flow path of the cooling water 1 introduced into the fluid passage part 40. Further, the discharge part 36 defines a main body discharge flow path 31 that becomes a flow path of the cooling water 1 discharged from the fluid passage part 40.

  The introduction pipe 47 is connected to the introduction part 35 of the main body part 30. Inside the introduction pipe 47, an introduction pipe flow path 41 which is a hollow region is formed. The introduction pipe 47 and the introduction part 35 constitute an introduction flow path part 83. The introduction channel part 83 defines an introduction channel 92 that guides the cooling water 1 to the fluid passage part 40. The main body introduction channel 85 and the introduction pipe channel 41 constitute an introduction channel 92. The discharge pipe 48 is connected to the discharge part 36 of the main body part 30.

  A hollow region 89 that is a through hole is formed in the main body 30. The hollow region 89 includes a main body introduction flow path 85, a main body discharge flow path 31, and a central flow path 96. The main body introduction flow path 85 and the main body discharge flow path 31 are connected by a central flow path 96. Unlike Embodiment 1, the cross-sectional area in the cross section perpendicular to the traveling direction 1a of the cooling water 1 in the hollow region 89 of the main body 30 is constant. The inner wall surfaces of the main body 30 facing each other with the hollow region 89 in between are parallel to each other.

  The fluid passage portion 40 is disposed in the central flow path 96 of the hollow region 89. The fluid passage part 40 is disposed so as to contact the heat transfer part 33 of the main body part 30. More specifically, the fluid passage part 40 contacts over the entire circumference of the inner wall surface of the heat transfer part 33. The heat transfer unit 33 defines a passage channel (a central channel 96) through which the cooling water 1 passes through the fluid passage unit 40 by surrounding the fluid passage unit 40.

  The fluid passage portion 40 includes an inflow surface 45 that is a surface into which the cooling water 1 is to flow and a discharge surface 46 that is a surface through which the cooling water 1 is to be discharged. In the cross section along the traveling direction 1a of the cooling water 1 (parallel to the traveling direction 1a), the inflow surface 45 and the discharge surface 46 are parallel. In the cross section, the fluid passage portion 40 has a parallelogram shape.

  The fluid passage part 40 is fixed by brazing to the inner wall surface of the heat transfer part 33, for example, as in the first embodiment. Moreover, the fluid passage part 40 consists of a metal porous body comprised from a metal with high heat conductivity. The fluid passage portion 40 has a porous structure through which the cooling water 1 can pass.

  The area of the inflow surface 45 of the fluid passage portion 40 is such that the introduction passage section 75a, which is a section of the introduction passage 92 perpendicular to the traveling direction 1a of the cooling water 1, flows along the traveling direction 1a of the cooling water 1. It is larger than the area of the introduction flow path cross section 75b located in the region adjacent to the upstream side of the inflow position 74, which is the position in contact with the fluid passage part 40 when approaching the passage part 40.

  More specifically, the inflow surface 45 is inclined with respect to the introduction channel cross section 75 c at the inflow position 74, so that the area of the inflow surface 45 is located in a region adjacent to the upstream side of the inflow position 74. It is larger than the area of the cross section 75b. When the inclination angle with respect to the introduction flow path section 75c at the inflow position 74 is (90−θ) °, the area of the inflow surface 45 is (1 / sin θ) times the area of the introduction flow path section 75b. That is, the inflow surface 45 is inclined so that the area of the inflow surface 45 is larger than the cross-sectional area of the main body introduction flow path 85. By having such a structure, in the heat sink 200 of the present embodiment, the speed of the cooling water 1 decreases before the cooling water 1 flows into the fluid passage portion 40. Therefore, the pressure loss can be reduced. As a result, the efficiency of heat exchange can be improved. Thus, according to the heat sink 200 in the present embodiment, in the heat sink 200 using the metal porous body, it is possible to reduce the pressure loss and improve the efficiency of heat exchange.

  Furthermore, unlike the case of the first embodiment, the heat sink 200 does not necessarily need to have a large cross-sectional area of the flow path of the cooling water 1 in the main body 30. Therefore, high heat exchange efficiency can be achieved even when used in applications where it is difficult to increase the size of the heat sink (heat exchanger) because of its structure.

(Embodiment 3)
Next, Embodiment 3 which is another embodiment will be described. Referring to FIG. 5, heat sink 300 that is a heat exchanger in the third embodiment is similar to the first embodiment in that main body 50, fluid passage 60, introduction pipe 68, and discharge A pipe 69 is provided, and the heat of the heat source is released by being similarly used.

  In the direction along the traveling direction 1 a of the cooling water 1, the main body 50 includes a heat transfer part 57 located in the center, an introduction part 55 located upstream from the heat transfer part 57, and the heat transfer part 57. And a discharge portion 56 located on the downstream side as viewed. The main body 50 is made of a metal having a high thermal conductivity such as copper. The main body 50 is in contact with a heat source (not shown) on the outer wall. The introduction part 55 defines a main body introduction flow path 86 that becomes a flow path of the cooling water 1 introduced into the fluid passage part 60. The discharge part 56 defines a main body discharge flow path 88 that becomes a flow path of the cooling water 1 discharged from the fluid passage part 60.

  The introduction pipe 68 is connected to the introduction part 55 of the main body part 50. An introduction pipe flow path 87 that is a hollow region is formed inside the introduction pipe 68. The introduction pipe 68 and the introduction part 55 constitute an introduction flow path part 84. The introduction channel portion 84 defines an introduction channel 93 that guides the cooling water 1 to the fluid passage portion 60. The main body introduction channel 86 and the introduction pipe channel 87 constitute an introduction channel 93. The discharge pipe 69 is connected to the discharge part 56 of the main body part 50.

  A hollow region 91 which is a through hole is formed in the main body 50. The hollow region 91 includes a main body introduction flow path 86, a main body discharge flow path 88, and a central flow path 97. The main body introduction flow path 86 and the main body discharge flow path 88 are connected by a central flow path 97. Unlike the case of the first embodiment, the cross-sectional area of the hollow region 91 in the cross section perpendicular to the traveling direction 1a of the cooling water 1 is constant.

  The fluid passage portion 60 is disposed in the hollow region 91 of the main body portion 50. The fluid passage part 60 is disposed so as to contact the heat transfer part 57 of the main body part 50. More specifically, the fluid passage portion 60 contacts over the entire circumference of the inner wall surface of the heat transfer portion 57. The heat transfer unit 57 defines a passage channel (central channel 97) for allowing the cooling water 1 to pass through the fluid passage unit 60 by surrounding the fluid passage unit 60.

  The fluid passage portion 60 includes an inflow surface 65 that is a surface into which the cooling water 1 is to flow and a discharge surface 95 that is a surface through which the cooling water 1 is to be discharged. The fluid passage portion 60 is fixed by brazing, for example, to the inner wall surface of the heat transfer portion 57 as in the case of the first embodiment. Moreover, the fluid passage part 60 consists of a metal porous body comprised from a metal with high heat conductivity. The fluid passage portion 60 has a porous structure through which the cooling water 1 can pass.

  Referring to FIG. 5, in heat sink 300 in the third embodiment, a plurality of upstream recesses 66 that are open on the upstream side and have a bottom wall inside are formed in fluid passage portion 60. In addition, the fluid passage portion 60 is formed with a plurality of downstream recesses 67 that are open on the downstream side and have a bottom wall inside the fluid passage portion 60 apart from the upstream recesses 66. That is, the downstream recess 67 does not communicate with the upstream recess 66. And the upstream recessed part 66 and the downstream recessed part 67 are alternately formed in the direction perpendicular | vertical to the advancing direction 1a of the cooling water 1 at equal intervals.

  Further, the distance L1 from the bottom wall of the upstream recess 66 to the downstream end of the fluid passage 60 is longer than the distance L2 between the adjacent upstream recess 66 and the downstream recess 67. As a result, the cooling water 1 flowing in from the opening of the upstream recess 66 of the fluid passage portion 60 flows into the adjacent downstream recess 67 and then flows from the opening of the downstream recess 67 to the discharge portion 56. The flow path can be controlled. In addition, in order to control the flow path of the cooling water 1, in addition to increasing the distance L1 from the bottom wall of the upstream recess 66 to the downstream end of the fluid passage portion 60, or instead of increasing the distance L1. The bottom wall of the upstream recess 66 may be sealed.

  The area of the inflow surface 65 of the fluid passage portion 60 is such that the introduction channel section 78a, which is a section of the introduction channel 93 perpendicular to the traveling direction 1a of the cooling water 1, flows along the traveling direction 1a of the cooling water 1. It is larger than the area of the introduction flow path cross section 78b located in the region adjacent to the upstream side of the inflow position 76, which is a position in contact with the fluid passage section 60 when approaching the passage section 60.

  More specifically, the upstream concave portion 66 having an opening on the upstream side and having a bottom wall inside is formed in the fluid passage portion 60, so that the area of the inflow surface 65 is adjacent to the upstream side of the inflow position 76. It is larger than the area of the introduction flow path section 78b located in the region where That is, the area of the inflow surface 65 is increased because the side wall surface of the upstream recess 66 functions as the inflow surface 65. By having such a structure, in the heat sink 300 of the present embodiment, the speed of the cooling water 1 decreases before the cooling water 1 flows into the fluid passage portion 60. Therefore, the pressure loss can be reduced. As a result, the efficiency of heat exchange can be improved. Thus, according to the heat sink 300 in the present embodiment, in the heat sink 300 using the porous metal body, it is possible to reduce the pressure loss and improve the efficiency of heat exchange.

  Furthermore, unlike the case of the first embodiment, the heat sink 300 does not necessarily have to increase the cross-sectional area of the flow path of the cooling water 1 in the main body 50. Therefore, high heat exchange efficiency can be achieved even when used in applications where it is difficult to increase the size of the heat sink (heat exchanger) because of its structure.

  In the heat sink 300 according to the third embodiment, both the upstream recess 66 and the downstream recess 67 are provided, but only the upstream recess 66 may be provided.

(Embodiment 4)
Next, a fourth embodiment which is still another embodiment will be described. Referring to FIGS. 6 and 7, heat sink 400 in the fourth embodiment has basically the same structure as in the first embodiment, and has the same effects. However, the heat sink 400 in the fourth embodiment is different from that in the first embodiment in that it further includes a heat conduction auxiliary member 5 made of a metal having a high thermal conductivity.

  Referring to FIGS. 6 and 7, in heat sink 400 in the fourth embodiment, heat conduction is arranged so as to connect region of fluid passage portion 20 located away from heat transfer portion 12 and heat transfer portion 12. An auxiliary member 5 is further provided. The heat conduction auxiliary member 5 is preferably arranged so as to connect the central part of the fluid passage part 20 and the heat transfer part 12. In the present embodiment, the heat conduction auxiliary member 5 is disposed so as to penetrate between the fluid passage portions 20 and connect the inner wall surfaces of the heat transfer portions 12 facing each other with the fluid passage portion 20 interposed therebetween. The heat conduction auxiliary member 5 has a columnar shape, for example, a columnar shape. As a material constituting the heat conduction auxiliary member 5, a metal having high heat conductivity, such as Cu, Al, or the like, can be employed.

  Thereby, in the fluid passage part 20, the movement of the heat between the area away from the contact surface of the heat transfer part 12 and the heat transfer part 12 becomes easy. As a result, the efficiency of heat exchange can be further improved.

  In addition, in this Embodiment, although the case where the heat conduction auxiliary member 5 was cylindrical shape was illustrated, other shapes, for example, thin plate shape, may be sufficient.

  Moreover, the structure of the heat exchanger in the said Embodiment 1-4 is a specific example in the structure of the heat exchanger of this application, Comprising: The structure of the heat exchanger of this application is not restricted to these. Therefore, for example, a structure in which the structures described in the first to fourth embodiments are appropriately combined may be employed.

  Moreover, in the said Embodiment 1-4, although the water-cooled heat sink was demonstrated as an example of the heat exchanger of this application, the heat exchanger of this application is not limited to this, The air heat exchange unit used for an air conditioning apparatus etc. It can be applied to various heat exchangers.

  A simulation for verifying the performance of the heat sink having the same structure as that of the first embodiment was performed. Specifically, in the same structure as in the first embodiment, the ratio of the cross-sectional area ratio of the cross-sectional area ratio of the inflow surface 25 to the area of the cross-section of the introductory flow path at the inlet from the introduction pipe 22 to the main body 10. ) Was assumed to be varied in the range of 6-60. Then, the relationship between the pressure loss and the thermal resistance in the heat sink was calculated by simulation (indicated as “cross-sectional area ratio 6 to 60” in FIG. 8). When water at a constant temperature flows into the heat sink 100 at a constant flow rate while the heat source is in contact with the outer wall of the main body 10, the amount of heat exchange with the heat source is calculated, and then the heat resistance is calculated. It was converted into a value and used as an index of the performance of the heat sink 100. The simulation was performed under the condition that the heat sink 100 and the heat source are insulated from the surrounding environment. The material of the fluid passage portion made of a metal porous body was assumed to be copper. The cross-sectional area of the flow path at the entrance to the main body 10 and the outlet from the main body 10 was constant. In addition, for comparison, a heat sink that does not use a fluid passage portion made of a metal porous body and that has improved thermal efficiency by optimizing the shape of the flow path was also simulated (see “ Comparative example ”). The result of the simulation is shown in FIG.

  In FIG. 8, the horizontal axis represents pressure loss, and the vertical axis represents thermal resistance. In the case of the cross-sectional areas of 6 to 18, characteristics corresponding to the case where the eye roughness of the fluid passage portion made of the metal porous body is changed are shown. Specifically, as the roughness of the fluid passage portion becomes smaller, the pressure loss increases and the thermal resistance decreases. In other words, it is understood that the pressure loss increases when the roughness of the fluid passage portion is reduced in order to reduce the thermal resistance. In order to improve the performance of the heat sink 100, it is preferable that pressure loss and thermal resistance are reduced. That is, in FIG. 8, it can be said that the data point is preferably directed toward the lower left.

  Referring to FIG. 8, it is confirmed that the performance of the heat sink improves as the cross-sectional area ratio increases. In addition, when the cross-sectional area ratio exceeds 18, it is understood that a performance that is difficult to reach with a heat sink that does not use a fluid passage portion made of a metal porous body is obtained. That is, it can be said that by adopting the structure in the first embodiment, a heat exchanger with excellent performance can be obtained.

  A simulation for verifying the performance of the heat sink having the same structure as that of the second embodiment was performed. Specifically, in the same structure as in the second embodiment, it is assumed that the inflow surface 45 is inclined in the direction opposite to that in FIG. 4 and the angle θ is 10 ° (model A). Then, when air at a constant temperature flows in at a constant flow rate, the heat transfer coefficient is calculated from the temperature change of the air in the fluid passage part 40, and this is calculated per unit volume of the fluid passage part 40 made of a metal porous body. This value was used as an index of the performance of the heat sink 200. In addition, the pressure loss in that case was also calculated. On the other hand, for comparison, the heat transfer coefficient per unit volume of the fluid passage portion 40 is also the same when the volume of the fluid passage portion and the length in the air flow direction are the same as those of the model A and θ is 90 °. Pressure loss was calculated (Model B). FIG. 9 shows a temperature distribution in the fluid passage portion 40 in the model A.

  In FIG. 9, white triangles indicate the air flow rate. Referring to FIG. 9, the temperature of air in fluid passage portion 40 is lowest in region A, and increases in the order of B, C, D, E, F, G, H, and I. Table 1 shows the pressure loss of the fluid passage portion 40 calculated from this temperature distribution and the heat transfer rate per unit volume.

Referring to Table 1, by inclining the inflow surface 45 so that the angle θ is 10 °, the pressure loss is reduced to about 1/6 while maintaining the heat transfer rate per unit volume of the fluid passage portion 40. It is confirmed that it can be reduced. Therefore, even when the space for installing the heat sink is limited, the heat sink performance is improved by reducing the pressure loss while maintaining the heat transfer rate by adopting the structure of the second embodiment. It can be said that this is possible.

  It should be understood that the embodiments disclosed herein are illustrative in all respects and are not restrictive in any aspect. The scope of the present invention is defined by the scope of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the scope of the claims.

DESCRIPTION OF SYMBOLS 1 Cooling water 1a Advancing direction 5 Heat conduction auxiliary member 10, 30, 50 Main body part 12, 33, 57 Heat transfer part 15 Main body introduction flow path 16 Main body discharge flow path 17 Central part 19, 89, 91 Hollow area 19 Hollow area 20 , 40, 60 Fluid passage part 22, 47, 68 Introduction pipe 23, 35 Introduction part 25, 45, 65 Inflow surface 27 Introduction pipe flow path 28, 48, 69 Discharge pipe 31 Main body discharge flow path 34, 36, 56 Discharge part 41, 87 Introduction pipe flow path 41 Introduction pipe flow path 46, 95 Discharge surface 55 Introduction part 66 Upstream concave part 67 Downstream concave part 70, 74, 76 Inflow positions 72a, 72b, 75a, 75b, 78a, 78b Introduction channel section 81, 83, 84 Introduction channel part 82, 92, 93 Introduction channel 85, 86 Main body introduction channel 88 Main body discharge channel 89 Hollow region 91 Hollow region 96 Central channel 97 Central channel 100, 200, 300, 400 heat sink

Claims (7)

A heat transfer section,
A fluid passage portion made of a metal porous body, arranged in contact with the heat transfer portion, and capable of allowing fluid to pass therethrough,
An introduction flow path section that defines an introduction flow path for guiding the fluid to the fluid passage section;
With
The area of the inflow surface, which is the surface into which the fluid flows in the fluid passage portion, is a cross-section of the introduction flow path that is a cross section of the introduction flow path perpendicular to the fluid traveling direction, along the fluid traveling direction. Greater than the area of the cross-section of the introduction channel located in the region adjacent to the upstream side of the inflow position, which is the position in contact with the fluid passage when close to the fluid passage
Heat exchanger. A heat conduction auxiliary member disposed so as to connect the region of the fluid passage part located away from the heat transfer part and the heat transfer part;
The heat exchanger according to claim 1. The heat transfer section defines a passage flow path for the fluid to pass through the fluid passage section by surrounding the fluid passage section.
The heat exchanger according to claim 1 or 2. Since the area of the cross section of the introduction flow path at the inflow position is larger than the area of the cross section of the introduction flow path located in a region adjacent to the upstream side of the inflow position, the area of the inflow surface is upstream of the inflow position. Is larger than the area of the cross section of the introduction channel located in the region adjacent to the side,
The heat exchanger according to any one of claims 1 to 3. The inflow surface is inclined with respect to the introduction channel cross section at the inflow position, so that the area of the inflow surface is larger than the area of the introduction channel cross section located in a region adjacent to the upstream side of the inflow position. Is getting bigger,
The heat exchanger according to any one of claims 1 to 4. The inflow area is located in a region adjacent to the upstream side of the inflow position by forming an upstream concave portion having an opening on the upstream side and having a bottom wall inside the fluid passage portion. Larger than the cross-sectional area of the channel,
The heat exchanger according to any one of claims 1 to 5. In the fluid passage portion, a downstream recess having an opening on the downstream side and having a bottom wall therein is formed apart from the upstream recess.
The heat exchanger according to claim 6.