Heat exchanger

Abstract

To provide a heat exchanger capable of improving the performance and efficiency of cooling a heating part.SOLUTION: A heat exchanger 1 includes a cooling container 10 and protrusions 20, the cooling container 10 being formed integrally with a heating component 2 or of a different member therefrom, and having a refrigerant flow path 11 where refrigerant flows from the refrigerant inlet 12 side to the refrigerant outlet 13 side, the protrusions 20 being provided on other faces 16, 17 different from a cooling face 14 on the side where the heating component 2 is arranged, out of the inner wall of the cooling container 10, and having a collision surface 23 and a guide surface 24, respectively, the collision surface 23 being provided in opposition to a main stream direction F1 heading from the refrigerant inlet 12 side to the refrigerant outlet 13 side, where the refrigerant flowing in the main stream direction F1 collides, the guide surface 24 extending from the outer edge of the collision surface 23 to the downstream side in the main stream direction for guiding a secondary flow F2 of the refrigerant formed after collision on the collision surface 23 to a site 15 right under the heating component 2 out of the cooling face 14.SELECTED DRAWING: Figure 4

Description

Technical Field

[0001] The present disclosure relates to a heat exchanger that performs heat exchange between a heat-generating component and a refrigerant.

Background Art

[0002] Patent Document 1 describes a boiling-cooling type heat exchanger that performs heat exchange between a heat-generating component and a refrigerant. This heat exchanger includes a heat dissipation plate provided in a refrigerant flow path, a tapered table fixed to the heat dissipation plate, and a plurality of heat dissipation fins provided on the tapered table. The heat-generating component is provided on the surface of the heat dissipation plate opposite to the refrigerant flow path. The tapered table is inclined so as to approach the center of the refrigerant flow path from the upstream side to the downstream side of the refrigerant flow path. Thereby, even when bubbles formed by boiling of the refrigerant adhere between the surface of the tapered table and the plurality of heat dissipation fins, the tapered table can detach those bubbles by the refrigerant whose flow direction is changed.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] However, in the heat exchanger described in Patent Document 1, the refrigerant flowing in the region of the refrigerant flow path that is away from the tapered table and the heat dissipation fins hardly contributes to the cooling of the heat-generating component. Therefore, this heat exchanger has a problem that the cooling performance for the heat-generating component is not sufficient. Further, this heat exchanger has a problem that the cooling amount of the heat-generating component with respect to the energy consumption of the pump that pumps the refrigerant into the refrigerant flow path is low, that is, the cooling efficiency for the heat-generating component is low.

[0005] In view of the above points, an object of the present disclosure is to provide a heat exchanger capable of improving the cooling performance and cooling efficiency for heat generating components.

Means for Solving the Problems

[0006] According to one aspect of the present disclosure, a heat exchanger that performs heat exchange between a heat generating component (2) and a refrigerant includes: a cooling container (10) that is integrally formed with or a separate member from the heat generating component and has a refrigerant flow path (11) through which the refrigerant flows from the refrigerant inlet (12) side to the refrigerant outlet (13) side; protrusions (20) provided on the other surfaces (16, 17) of the inner wall of the cooling container that are different from the cooling surface (14) on the side where the heat generating component is disposed; The protrusion is: a collision surface (23) provided facing the main flow direction (F1) from the refrigerant inlet side to the refrigerant outlet side, against which the refrigerant flowing in the main flow direction collides; a guide surface (24) that extends from the outer edge of the collision surface to the downstream side in the main flow direction and guides the secondary flow (F2) of the refrigerant formed by the collision on the collision surface toward the portion (15) directly below the heat generating component of the cooling surface.

[0007] According to this, the refrigerant flowing through the refrigerant flow path from the refrigerant inlet collides with the collision surface to form a secondary flow. Then, the secondary flow is guided by the guide surface and collides with the portion (hereinafter referred to as the "high temperature portion") directly below the heat generating component of the cooling surface. Therefore, the heat transfer rate from the high temperature portion to the refrigerant increases, and the cooling performance for the heat generating component can be improved. In addition, the secondary flow that has collided with the high temperature portion becomes a swirling flow that swirls in the refrigerant flow path, the velocity boundary layer becomes thinner, the fluid mixing action is promoted, and the heat transfer from the high temperature portion to the refrigerant is promoted. Furthermore, by forming a secondary flow throughout the refrigerant flow path, the refrigerant that does not contribute to the cooling of the heat generating component among the refrigerant flowing through the refrigerant flow path decreases, and the cooling efficiency of the heat generating component can be improved.

[0008] Note that the reference numerals in parentheses attached to each component, etc., indicate an example of the correspondence relationship between the component, etc., and the specific components, etc., described in the embodiments described later.

Brief Description of the Drawings

[0009]

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Embodiments for Carrying Out the Invention

[0010] Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In the following embodiments, parts that are identical or equivalent to each other are denoted by the same reference numerals, and the description thereof will be omitted.

[0011] (First Embodiment) The first embodiment will be described. As shown in FIG. 1, the heat exchanger 1 of the first embodiment is used in a boiling cooling system 3 for cooling a heat generating component 2. The heat generating component 2 is, for example, a semiconductor element that generates heat by energization. The semiconductor element is, for example, a MOSFET or an IGBT, etc.

[0012] First, the boiling cooling system 3 in which the heat exchanger 1 of the first embodiment is used will be described. As shown in FIG. 1, the boiling cooling system 3 includes a heat exchanger 1, a pump 4, a radiator 5, a refrigerant pipe 6, etc. The refrigerant circulating in the boiling cooling system 3 may be, for example, water, or a liquid having electrical insulation properties such as LLC (abbreviation for Long Life Coolant), or a fluorine-based inert liquid. The refrigerant is pressure-adjusted so that its boiling point is sufficiently lower than the average temperature during the operation of the heat generating component 2.

[0013] The pump 4 sucks in a liquid-rich refrigerant and sends the refrigerant toward the heat exchanger 1. Note that the liquid-rich refrigerant means not only a liquid single-phase liquid refrigerant but also includes a liquid-rich gas-liquid two-phase refrigerant (for example, a dryness of 0 to 0.2).

[0014] The heat exchanger 1 performs heat exchange between the refrigerant flowing through the refrigerant flow path 11 formed inside the cooling container 10 and the heat generating component 2. The heat generated by the heat generating component 2 is absorbed by the refrigerant. The refrigerant flowing out of the heat exchanger 1 flows into the radiator 5. The radiator 5 dissipates the heat of the refrigerant to the outside air or a predetermined heat medium.

[0015] Next, the configuration of the heat exchanger 1 of the first embodiment will be described.

[0016] As shown in FIGS. 2 to 6, the heat exchanger 1 includes a cooling container 10 and a protrusion 20. The cooling container 10 is formed of, for example, a metal or resin having excellent heat conductivity. The cooling container 10 may be configured as a separate member from the heat generating component 2, or may be integrally formed with the heat generating component 2. Further, the cooling container 10 may be configured by joining a plurality of members 10a and 10b at an arbitrary position, or may be configured by a single member. In the refrigerant flow path 11 of the cooling container 10, the refrigerant flows from the refrigerant inlet 12 side to the refrigerant outlet 13 side. The direction from the refrigerant inlet 12 side to the refrigerant outlet 13 side in the refrigerant flow path 11 is referred to as the "main flow direction F1".

[0017] In the following description, among the inner walls of the cooling container 10, the surface on the side where the heat generating component 2 is disposed is referred to as the "cooling surface 14". Among the cooling surface 14, the portion directly below the heat generating component 2 is referred to as the "high temperature portion 15". Note that the portion directly below the heat generating component 2 refers to the portion where the heat generating component 2 is projected onto the cooling surface 14. In FIG. 6, the high temperature portion 15 is indicated by a dashed line. The high temperature portion 15 is a portion that becomes higher than the boiling point of the refrigerant due to the heat generation of the heat generating component 2. On the other hand, among the inner walls of the cooling container 10, the surface different from the cooling surface 14 is referred to as the "other surface". Among the other surfaces, the surface facing the cooling surface 14 is referred to as the "opposing surface 16", and the surface facing in a direction perpendicular to the direction in which the cooling surface 14 and the opposing surface 16 face each other is referred to as the "side surface 17".

[0018] In the first embodiment, the protrusion 20 is provided at a position on the opposing surface 16 corresponding to the heat generating component 2. In other words, the protrusion 20 is located at a portion of the opposing surface 16 in the direction in which the cooling surface 14 and the opposing surface 16 face each other with respect to the heat generating component 2. The protrusion 20 protrudes from the opposing surface 16 toward the cooling surface 14. The protrusion 20 has a shape that gradually becomes thinner from the opposing surface 16 side toward the cooling surface 14 side. In other words, the protrusion 20 has a shape in which the cross-sectional area perpendicular to the protruding direction from the opposing surface 16 gradually decreases from the opposing surface 16 side toward the cooling surface 14 side. Among the protrusions 20, the portion farthest from the opposing surface 16 is referred to as the "protrusion tip portion 21". On a virtual plane 22 connecting the center of the portion of the protrusion 20 on the opposing surface 16 side and the protrusion tip portion 21, there is a high-temperature portion 15 of the cooling surface 14. In the following description, the virtual plane 22 connecting the center of the portion of the protrusion 20 on the opposing surface 16 side and the protrusion tip portion 21 is referred to as the "protrusion center plane 22".

[0019] The protrusion 20 has a collision surface 23 and a guide surface 24. The collision surface 23 is a surface facing the main flow direction F1. Therefore, the refrigerant flowing through the refrigerant flow path 11 from the refrigerant inlet 12 side collides with the collision surface 23 in the main flow direction F1. In the first embodiment, the collision surface 23 is provided substantially perpendicular to the main flow direction F1. As will be described in the 21st and 22nd embodiments described later, the collision surface 23 may be inclined at a predetermined angle (for example, 45° to 135°) with respect to the main flow direction F1.

[0020] The guide surface 24 is a surface extending from both sides of the outer edge of the collision surface 23 to the downstream side in the main flow direction F1. Further, the guide surfaces 24 are formed on the left and right of the protrusion 20 and are surfaces connecting the protrusion tip portion 21 and the opposing surface 16. The guide surface 24 guides the secondary flow F2 of the refrigerant formed by the collision on the collision surface 23 toward the high-temperature portion 15 of the cooling surface 14. In the first embodiment, both the left and right guide surfaces 24 are formed in a curved surface shape that is concave toward the protrusion center plane 22 side.

[0021] Subsequently, the flow of the refrigerant flowing through the refrigerant flow path 11 in the heat exchanger 1 of the first embodiment and its action will be described.

[0022] As shown in FIGS. 3 to 6, when the refrigerant flowing in the refrigerant flow path 11 from the refrigerant inlet 12 side in the main flow direction F1 collides with the collision surface 23 of the protrusion 20, the direction of the flow changes toward the cooling surface 14 side, forming a secondary flow F2. The secondary flow F2 is guided by the left and right guide surfaces 24 toward the high-temperature portion 15 of the cooling surface 14 and collides with the high-temperature portion 15. Then, the secondary flow F2 that has collided with the high-temperature portion 15 becomes a swirling flow that swirls in the regions on the right side and the left side of the protrusion 20 in the refrigerant flow path 11 and flows toward the refrigerant outlet 13 side.

[0023] The refrigerant that has collided with the high-temperature portion 15 absorbs heat from the high-temperature portion 15 and boils when its temperature becomes higher than the boiling point. The bubbles generated by the boiling of the refrigerant are separated from the high-temperature portion 15 by the swirling flow, agitated with the liquid-phase refrigerant by the swirling flow, and condensation is promoted. Therefore, it is possible to cause a liquid-rich refrigerant to collide with the high-temperature portion 15. Accordingly, the heat generated by the heat-generating component 2 is absorbed by the refrigerant from the high-temperature portion 15, and the cooling of the heat-generating component 2 is promoted.

[0024] The heat exchanger 1 of the first embodiment described above has the following operating effects.

[0025] (1) In the first embodiment, the heat exchanger 1 includes a protrusion 20 provided on the opposing surface 16 of the inner wall of the cooling container 10. The protrusion 20 has a collision surface 23 against which the refrigerant flowing in the main flow direction F1 collides and a guide surface 24 that guides the secondary flow F2 of the refrigerant toward the high-temperature portion 15 of the cooling surface 14. According to this, the refrigerant flowing through the refrigerant flow path 11 from the refrigerant inlet 12 collides with the collision surface 23, forming the secondary flow F2. Then, the secondary flow F2 is guided by the guide surface 24 and collides with the high-temperature portion 15 of the cooling surface 14. Therefore, the heat transfer rate from the high-temperature portion 15 to the refrigerant increases, and the cooling performance for the heat-generating component 2 can be improved. In addition, the secondary flow F2 that has collided with the high-temperature portion 15 becomes a swirling flow that swirls in the refrigerant flow path 11, the velocity boundary layer becomes thinner, the fluid mixing action is promoted, and the heat transfer from the high-temperature portion 15 to the refrigerant is promoted. Furthermore, by forming the secondary flow F2 throughout the refrigerant flow path 11, the refrigerant that does not contribute to the cooling of the heat-generating component 2 among the refrigerant flowing through the refrigerant flow path 11 is reduced, and the cooling efficiency of the heat-generating component 2 can be improved.

[0026] (2) In the first embodiment, the protrusion 20 has a shape that gradually becomes thinner as it moves away from the opposing surface 16. According to this, two swirling flows (i.e., secondary flows F2) can be formed in the refrigerant flow path 11 by the two guide surfaces 24 provided on the left and right of the protrusion 20, and these secondary flows F2 can be guided toward the high-temperature portion 15. Therefore, when these secondary flows F2 collide with the high-temperature portion 15, the heat transfer rate from the high-temperature portion 15 to the refrigerant increases, and the cooling performance for the heat-generating component 2 can be improved.

[0027] (3) In the first embodiment, both of the left and right guide surfaces 24 of the protrusion 20 are curved surfaces that are concave toward the protrusion center plane 22. According to this, by forming the guide surface 24 for guiding the secondary flow F2 of the refrigerant into a curved surface shape, the pressure loss of the refrigerant can be reduced. Therefore, the secondary flow F2 with a high flow rate can be made to collide with the high-temperature portion 15 to improve the cooling performance.

[0028] (4) In the first embodiment, the protrusion 20 is provided on the opposing surface 16. According to this, since both of the two secondary flows F2 respectively formed on the left and right of the protrusion 20 can be made to collide with the high-temperature portion 15, the cooling performance for the heat-generating component 2 can be improved. Also, the refrigerant that does not contribute to the cooling of the heat-generating component 2 among the refrigerant flowing through the refrigerant flow path 11 is reduced, and the cooling efficiency of the heat-generating component 2 can be improved.

[0029] (5) In the first embodiment, the high-temperature portion 15 of the cooling surface 14 is on the protrusion center plane 22. According to this, the secondary flow F2 guided by the guide surface 24 can be made to directly collide with the high-temperature portion 15, the heat transfer rate from the high-temperature portion 15 to the refrigerant increases, and the cooling performance for the heat-generating component 2 can be improved.

[0030] (Second to Fourth Embodiments) The second to fourth embodiments are those in which the shape of the guide surface 24 of the protrusion 20 is changed with respect to the first embodiment, and since the rest is the same as the first embodiment, only the parts different from the first embodiment will be described.

[0031] (Second Embodiment) The second embodiment will be described. As shown in FIG. 7, the guide surface 24 of the protrusion 20 included in the heat exchanger 1 of the second embodiment is flat. The protrusion 20 has a shape that gradually becomes thinner as it moves away from the opposing surface 16. That is, the protrusion 20 has a triangular cross-section perpendicular to the main flow direction F1. In that triangular shape, the inner angle θ1 between one guide surface 24 and the opposing surface 16 is different from the inner angle θ2 between the other guide surface 24 and the opposing surface 16. However, those inner angles θ1 and θ2 are set such that the high-temperature portion 15 of the cooling surface 14 is located on the protrusion center plane 22. Therefore, the guide surface 24 can guide the secondary flow F2 of the refrigerant formed by the collision at the collision surface 23 toward the high-temperature portion 15 of the cooling surface 14.

[0032] The heat exchanger 1 of the second embodiment described above can also achieve the same operational effects as the first embodiment. Note that the protrusion 20 may have the same inner angles θ1 and θ2 of the triangular shape.

[0033] (Third Embodiment) The third embodiment will be described. As shown in FIG. 8, the guide surface 24 of the protrusion 20 included in the heat exchanger 1 of the third embodiment is formed in a curved surface shape that is convex outward from the protrusion center plane 22 (that is, toward the side surface 17 side or the cooling surface 14 side). The protrusion 20 has a shape that gradually becomes thinner as it moves away from the opposing surface 16. And there is a high-temperature portion 15 of the cooling surface 14 on the protrusion center plane 22. Therefore, the guide surface 24 can guide the secondary flow F2 of the refrigerant formed by the collision at the collision surface 23 toward the high-temperature portion 15 of the cooling surface 14.

[0034] The heat exchanger 1 of the third embodiment described above can also achieve the same operational effects as the first embodiment.

[0035] (Fourth Embodiment) The fourth embodiment will be described. As shown in FIG. 9, the guide surface 24 of the protrusion 20 included in the heat exchanger 1 of the fourth embodiment has a curved surface portion that is convexly curved outward (i.e., toward the side surface 17 side or the cooling surface 14 side) from the protrusion center plane 22, and a curved surface portion that is concavely curved toward the protrusion center plane 22 side continuously. This protrusion 20 also has a shape that gradually becomes thinner as it moves away from the opposing surface 16. And, on the protrusion center plane 22, there is a high-temperature portion 15 of the cooling surface 14. Therefore, the guide surface 24 can guide the secondary flow F2 of the refrigerant formed by the collision at the collision surface 23 toward the high-temperature portion 15 of the cooling surface 14.

[0036] The heat exchanger 1 of the fourth embodiment described above can also achieve the same operational effects as those of the first embodiment.

[0037] (Fifth to Seventh Embodiments) In the fifth to seventh embodiments, fine concavo-convex grooves 30 are provided on the guide surface 24 of the protrusion 20 or the inner wall of the cooling container 10 with respect to the first embodiment, and since the other aspects are the same as those of the first embodiment, only the parts different from the first embodiment will be described.

[0038] (Fifth Embodiment) The fifth embodiment will be described. As shown in FIGS. 10 to 12, the heat exchanger 1 of the fifth embodiment includes fine concavo-convex grooves 30 on the guide surface 24 of the protrusion 20. The fine concavo-convex grooves 30 are fine concavo-convex grooves extending in a direction intersecting the main flow direction F1. Specifically, the fine concavo-convex grooves 30 provided on the guide surface 24 of the protrusion 20 extend from the refrigerant inlet 12 side toward the refrigerant outlet 13 side and in a direction inclined from the opposing surface 16 side toward the cooling surface 14 side. That is, the fine concavo-convex grooves 30 provided on the guide surface 24 of the protrusion 20 extend in a direction approximating the direction of the secondary flow F2 flowing in the vicinity of the guide surface 24.

[0039] As shown in FIG. 13, the cross-sectional shape of the unevenness forming the fine uneven groove 30 may be, for example, triangular. The pitch P, depth D, angle θ3, and cross-sectional shape of the unevenness forming the fine uneven groove 30 are appropriately designed to strengthen the secondary flow F2 according to the physical properties of the refrigerant (for example, kinematic viscosity coefficient, etc.) and the flow velocity through experiments and simulations. This is the same for the modified examples of the fifth embodiment, the sixth and seventh embodiments, and their modified examples described later. The fine uneven groove 30 can be formed, for example, by cutting or plastic working.

[0040] In the fifth embodiment described above, the guide surface 24 of the protrusion 20 has the fine uneven groove 30 extending in a direction intersecting the main flow direction F1. According to this, by forming the flow F3 that strengthens the secondary flow F2 in the vicinity of the guide surface 24, the secondary flow F2 formed in the refrigerant flow path 11 can be strengthened, and the cooling performance for the heat generating component 2 can be improved.

[0041] (Modified Example of the Fifth Embodiment) A modified example of the fifth embodiment will be described. As shown in FIG. 14, the cross-sectional shape of the unevenness forming the fine uneven groove 30 may be, for example, quadrangular.

[0042] Note that the cross-sectional shape of the unevenness forming the fine uneven groove 30 is not limited to the above-described triangle and quadrangle, and can be arbitrarily set, for example, an arc shape. This is the same for the sixth and seventh embodiments and their modified examples described later.

[0043] (Sixth Embodiment) The sixth embodiment will be described. As shown in FIGS. 15 to 17, the heat exchanger 1 of the sixth embodiment includes fine concavo-convex grooves 30 on the cooling surface 14. The fine concavo-convex grooves 30 extend in a direction intersecting the main flow direction F1. Specifically, as shown in FIG. 17, the fine concavo-convex grooves 30 provided on the right side of the position on the protrusion center plane 22 of the cooling surface 14 extend from the position on the protrusion center plane 22 toward the right side surface 17 and are inclined and extend from the refrigerant inlet 12 side to the refrigerant outlet 13 side. On the other hand, the fine concavo-convex grooves 30 provided on the left side of the position on the protrusion center plane 22 of the cooling surface 14 extend from the position on the protrusion center plane 22 toward the left side surface 17 and are inclined and extend from the refrigerant inlet 12 side to the refrigerant outlet 13 side. That is, the fine concavo-convex grooves 30 provided on the cooling surface 14 extend in a direction approximating the direction of the secondary flow F2 flowing in the vicinity of the cooling surface 14.

[0044] In the sixth embodiment described above, the cooling surface 14 has fine concavo-convex grooves 30 extending in a direction intersecting the main flow direction F1. According to this, by forming a flow F3 that strengthens the secondary flow F2 in the vicinity of the cooling surface 14, the secondary flow F2 formed in the refrigerant flow path 11 can be strengthened, and the cooling performance for the heat generating component 2 can be improved. Further, by increasing the surface area of the cooling surface 14, the heat transfer rate from the high temperature portion 15 to the refrigerant increases, and the cooling performance for the heat generating component 2 can be improved.

[0045] Note that the fine concavo-convex grooves 30 are not limited to the configuration provided on the entire surface of the cooling surface 14, and may be provided, for example, on a part of the cooling surface 14 including the high temperature portion 15.

[0046] (Modification of the Sixth Embodiment) A modification of the sixth embodiment will be described. As shown in FIG. 18, the fine concavo-convex grooves 30 provided on the cooling surface 14 extend in a direction orthogonal to the main flow direction F1. Even in this case, a flow F3 that strengthens the secondary flow F2 can be formed in the vicinity of the cooling surface 14, the secondary flow F2 formed in the refrigerant flow path 11 can be strengthened, and the cooling performance for the heat generating component 2 can be improved. Further, by increasing the surface area of the cooling surface 14, the heat transfer rate from the high temperature portion 15 to the refrigerant increases, and the cooling performance for the heat generating component 2 can be improved.

[0047] (Embodiment 7) Embodiment 7 will be described. As shown in FIGS. 19 and 20, the heat exchanger 1 of Embodiment 7 includes the fine uneven grooves 30 on all surfaces of the inner wall of the cooling container 10 (i.e., the cooling surface 14, the opposing surface 16, and the side surface 17) and the guide surface 24 of the protrusion 20. The fine uneven grooves 30 extend in a direction intersecting the main flow direction F1. Thereby, by forming the flow F3 that strengthens the secondary flow F2 in the vicinity of all surfaces of the inner wall of the cooling container 10 and the guide surface 24, the secondary flow F2 formed in the refrigerant flow path 11 is strengthened, and the cooling performance for the heat generating component 2 can be improved.

[0048] In Embodiment 7 described above, in addition to the cooling surface 14 of the inner wall of the cooling container 10, the fine uneven grooves 30 are also provided on the other surfaces (i.e., the opposing surface 16 and the side surface 17). According to this, by forming the flow F3 that strengthens the secondary flow F2 not only in the vicinity of the cooling surface 14 of the inner wall of the cooling container 10 but also in the vicinity of the other surfaces, the secondary flow F2 formed in the refrigerant flow path 11 is strengthened, and the cooling performance for the heat generating component 2 can be improved.

[0049] Furthermore, in Embodiment 7, it is preferable that the pitch of the unevenness forming the fine uneven grooves 30 of the guide surface 24 of the protrusion 20 and the pitch of the unevenness forming the fine uneven grooves 30 of the cooling surface 14 are the same or an integral multiple. According to this, the refrigerant can be efficiently introduced into the grooves of the fine uneven grooves 30, the secondary flow F2 flowing from the guide surface 24 to the cooling surface 14 is strengthened, and the cooling performance for the heat generating component 2 can be improved.

[0050] (Embodiments 8 to 10) Embodiments 8 to 10 are those in which the protrusion 20 is provided on the side surface 17 of the inner wall of the cooling container 10 with respect to Embodiment 1, and since the other aspects are the same as those of Embodiment 1, only the parts different from Embodiment 1 will be described.

[0051] (Embodiment 8) The eighth embodiment will be described. As shown in FIG. 21, in the eighth embodiment, a protrusion 20 is provided on the left side surface 17 of the cooling container 10 when viewed from the upstream side. The protrusion 20 protrudes from the left side surface 17 toward the right side surface 17. The protrusion 20 has a shape that gradually narrows from the left side surface 17 toward the right side surface 17.

[0052] As shown in FIG. 21, when the refrigerant flowing in the refrigerant flow path 11 in the main flow direction F1 from the refrigerant inlet 12 side collides with the collision surface 23 of the protrusion 20, the flow direction is changed to form a secondary flow F2. The secondary flow F2 is guided by the guide surface 24 to form two swirling flows in the refrigerant flow path 11. Among the two swirling flows, the swirling flow formed on the cooling surface 14 side from the protrusion center plane 22 can improve the cooling performance for the heat generating component 2.

[0053] (Ninth Embodiment) The ninth embodiment will be described. As shown in FIG. 22, also in the ninth embodiment, the protrusion 20 is provided on the left side surface 17. The protrusion 20 protrudes from the left side surface 17 toward the high temperature portion 15. The protrusion 20 has a shape that gradually narrows from the left side surface 17 toward the high temperature portion 15. Therefore, in the ninth embodiment, the high temperature portion 15 is on the protrusion center plane 22.

[0054] As shown in FIG. 22, when the refrigerant flowing in the refrigerant flow path 11 in the main flow direction F1 from the refrigerant inlet 12 side collides with the collision surface 23 of the protrusion 20, the flow direction is changed to form a secondary flow F2. The secondary flow F2 is guided by the guide surface 24 toward the high temperature portion 15 of the cooling surface 14 and collides with the high temperature portion 15. Then, the secondary flow F2 that has collided with the high temperature portion 15 becomes two swirling flows that swirl in the regions on the right side and the left side of the protrusion center plane 22 in the refrigerant flow path 11, respectively.

[0055] In the ninth embodiment described above, since the secondary flow F2 of the refrigerant directly collides with the high temperature portion 15, the heat transfer rate from the high temperature portion 15 to the refrigerant increases, and the cooling performance for the heat generating component 2 can be improved. Also, both of the two secondary flows F2 can be used to cool the heat generating component 2. Furthermore, in the ninth embodiment, since the protrusion 20 can form the secondary flow F2 regardless of whether it is provided on the opposing surface 16 or the side surface 17, it can be easily processed even if it has a complex shape, and it has excellent manufacturability.

[0056] (Tenth Embodiment) The tenth embodiment will be described. As shown in FIG. 23, in the tenth embodiment, two protrusions 20 are provided on the left side surface 17 and the right side surface 17, respectively. One protrusion 20 protrudes from the left side surface 17 toward the high-temperature portion 15, and the other protrusion 20 protrudes from the right side surface 17 toward the high-temperature portion 15. Both of the two protrusions 20 have a shape that gradually narrows from the left side surface 17 toward the high-temperature portion 15. Therefore, in the tenth embodiment, the high-temperature portion 15 is located on the protrusion center plane 22 of both of the two protrusions 20.

[0057] As shown in FIG. 23, when the refrigerant flowing in the refrigerant flow path 11 in the main flow direction F1 from the refrigerant inlet 12 side collides with the collision surface 23 of the two protrusions 20, the direction of the flow is changed to form the secondary flow F2. The secondary flow F2 is guided by the guide surfaces 24 of the two protrusions 20 toward the high-temperature portion 15 of the cooling surface 14 and collides with the high-temperature portion 15. Then, the secondary flow F2 that has collided with the high-temperature portion 15 becomes a swirling flow that swirls in the refrigerant flow path 11.

[0058] In the tenth embodiment described above, since the secondary flow F2 of the refrigerant formed by each of the two protrusions 20 collides with the high-temperature portion 15, the heat transfer rate from the high-temperature portion 15 to the refrigerant increases, and the cooling performance for the heat-generating component 2 can be further improved. Furthermore, also in the tenth embodiment, since the protrusion 20 can form the secondary flow F2 regardless of whether it is provided on the opposing surface 16 or the side surface 17, it can be easily processed even if it has a complex shape, and it has excellent manufacturability.

[0059] (Eleventh to Fourteenth Embodiments) In the 11th to 14th embodiments, a plurality of protrusions 20 are provided in the cooling container 10 with respect to the first embodiment, and since the other aspects are the same as those of the first embodiment, only the parts different from the first embodiment will be described.

[0060] (11th Embodiment) The 11th embodiment will be described. As shown in FIGS. 24 to 26, in the 11th embodiment, a plurality of heat-generating components 2a and 2b are provided in the cooling container 10. The cooling container 10 and the plurality of heat-generating components 2a and 2b may be constituted by separate members, or they may be integrally constituted. The plurality of heat-generating components 2a and 2b are arranged in series in the mainstream direction F1. In the following description, among the plurality of heat-generating components 2a and 2b, the one arranged on the upstream side in the mainstream direction F1 is called the first heat-generating component 2a, and the one arranged on the downstream side is called the second heat-generating component 2b.

[0061] In the refrigerant flow path 11 inside the cooling container 10, a plurality of protrusions 20a and 20b are provided at positions corresponding to the plurality of heat-generating components 2a and 2b, respectively. In the following description, among the plurality of protrusions 20a and 20b, the one arranged on the upstream side in the mainstream direction F1 is called the first protrusion 20a, and the one arranged on the downstream side is called the second protrusion 20b. Specifically, the first protrusion 20a is located at a part of the opposing surface 16 in the direction in which the cooling surface 14 and the opposing surface 16 face each other with respect to the first heat-generating component 2a. The second protrusion 20b is located at a part of the opposing surface 16 in the direction in which the cooling surface 14 and the opposing surface 16 face each other with respect to the second heat-generating component 2b. Therefore, the first protrusion 20a and the second protrusion 20b are arranged in series.

[0062] Both of the plurality of protrusions 20a and 20b protrude from the opposing surface 16 toward the cooling surface 14. The protrusions 20a and 20b have a shape that gradually becomes thinner from the opposing surface 16 side toward the cooling surface 14 side. The first heat-generating component 2a is on the protrusion center plane 22 of the first protrusion 20a, and the second heat-generating component 2b is on the protrusion center plane 22 of the second protrusion 20b.

[0063] As shown in FIGS. 25 and 26, when the refrigerant flowing through the refrigerant flow path 11 from the refrigerant inlet 12 side in the main flow direction F1 collides with the collision surface 23a of the first protrusion 20a, the direction of the flow changes toward the cooling surface 14 side, forming a secondary flow F2. The secondary flow F2 is guided by the guide surface 24a of the first protrusion 20a toward the high-temperature portion 15a directly below the first heat-generating component 2a, collides with the high-temperature portion 15a, and becomes a swirling flow that swirls in the refrigerant flow path 11. Next, when the refrigerant flowing downstream from the first protrusion 20a collides with the collision surface 23b of the second protrusion 20b, the direction of the flow changes toward the cooling surface 14 side, forming a secondary flow F2. The secondary flow F2 is guided by the guide surface 24b of the second protrusion 20b toward the high-temperature portion 15b directly below the second heat-generating component 2b, collides with the high-temperature portion 15b, becomes a swirling flow that swirls in the refrigerant flow path 11, and flows toward the refrigerant outlet 13.

[0064] In the 11th embodiment described above, the plurality of protrusions 20a and 20b are provided at positions corresponding to the plurality of heat-generating components 2a and 2b, respectively. According to this, the plurality of protrusions 20a and 20b can each form a secondary flow F2 that collides with the plurality of high-temperature portions 15a and 15b corresponding to the plurality of heat-generating components 2a and 2b. Therefore, even in a long refrigerant flow path 11 that cools the plurality of heat-generating components 2a and 2b simultaneously, by maintaining the formation of the secondary flow F2, not only the upstream heat-generating component 2a but also the downstream heat-generating component 2b can be efficiently cooled.

[0065] (12th Embodiment) The 12th embodiment will be described. As shown in FIGS. 27 to 30, also in the 12th embodiment, a plurality of heat-generating components 2a and 2b are provided in the cooling container 10. The plurality of heat-generating components 2a and 2b are arranged in a staggered manner with respect to the main flow direction F1.

[0066] In the refrigerant flow path 11 inside the cooling container 10, a plurality of protrusions 20a and 20b are provided at positions corresponding to a plurality of heat generating components 2a and 2b, respectively. Specifically, the first protrusion 20a is located at a portion of the opposing surface 16 in the direction in which the cooling surface 14 and the opposing surface 16 face each other with respect to the first heat generating component 2a. The second protrusion 20b is located at a portion of the opposing surface 16 in the direction in which the cooling surface 14 and the opposing surface 16 face each other with respect to the second heat generating component 2b. Therefore, the plurality of protrusions 20a and 20b are arranged in a staggered manner, similar to the plurality of heat generating components 2a and 2b.

[0067] Both of the plurality of protrusions 20a and 20b protrude from the opposing surface 16 toward the cooling surface 14. The first heat generating component 2a is located on the protrusion center plane 22a of the first protrusion 20a, and the second heat generating component 2b is located on the protrusion center plane 22b of the second protrusion 20b.

[0068] The heat exchanger 1 of the 12th embodiment described above also exhibits the same operational effects as the 11th embodiment. That is, even if the plurality of heat generating components 2a and 2b are not arranged in a straight line, the plurality of heat generating components 2a and 2b can be efficiently cooled.

[0069] (13th Embodiment) The 13th embodiment will be described. As shown in FIGS. 31 to 33, in the 13th embodiment, one heat generating component 2 is provided in the cooling container 10. On the other hand, in the refrigerant flow path 11 inside the cooling container 10, a plurality of protrusions 20c and 20d are provided at positions corresponding to the one heat generating component 2. In the following description, among the plurality of protrusions 20c and 20d, the one arranged on the right side when viewing the cooling container 10 from the upstream side is referred to as the right protrusion 20c, and the one arranged on the left side is referred to as the left protrusion 20d. The right protrusion 20c and the left protrusion 20d are arranged side by side in a direction orthogonal to the main flow direction F1.

[0070] As shown in FIGS. 32 and 33, when the refrigerant flowing in the refrigerant flow path 11 from the refrigerant inlet 12 side in the main flow direction F1 collides with the collision surface 23c of the right protrusion 20c and the collision surface 23d of the left protrusion 20d, the flow direction is changed toward the cooling surface 14 side, and secondary flows F2 are respectively formed. These secondary flows F2 are guided toward the high-temperature portion 15 by the guide surface 24c of the right protrusion 20c and the guide surface 24d of the left protrusion 20d, and collide with the high-temperature portion 15. The secondary flow F2 that has collided with the high-temperature portion 15 becomes a swirling flow that swirls in the refrigerant flow path 11 and flows toward the refrigerant outlet 13.

[0071] In the 13th embodiment described above, a plurality of protrusions 20c and 20d are provided for one heat-generating component 2. According to this, by colliding the refrigerant against the high-temperature portion 15 directly below one heat-generating component 2 with the secondary flows F2 formed by the plurality of protrusions 20c and 20d, the cooling performance for the heat-generating component 2 can be improved. Further, by forming a large number of swirling flows with the plurality of protrusions 20c and 20d, there is an effect of strengthening the swirling flow in the refrigerant flow path 11, and the cooling performance can be improved.

[0072] (14th Embodiment) The 14th embodiment will be described. As shown in FIGS. 34 to 36, also in the 14th embodiment, a plurality of heat-generating components 2c and 2d are provided in the cooling container 10. The plurality of heat-generating components 2c and 2d are arranged in parallel with respect to the main flow direction F1. In other words, the plurality of heat-generating components 2c and 2d are arranged in a direction orthogonal to the main flow direction F1. In the following description, among the plurality of heat-generating components 2c and 2d, the one arranged on the right side when viewed from the upstream side is referred to as the right heat-generating component 2c, and the one arranged on the left side is referred to as the left heat-generating component 2d.

[0073] In the refrigerant flow path 11 inside the cooling container 10, a plurality of protrusions 20c and 20d are provided at positions corresponding to a plurality of heat generating components 2c and 2d, respectively. Specifically, the right protrusion 20c is located at a portion of the opposing surface 16 in the direction in which the cooling surface 14 and the opposing surface 16 face each other with respect to the right heat generating component 2c. The left protrusion 20d is located at a portion of the opposing surface 16 in the direction in which the cooling surface 14 and the opposing surface 16 face each other with respect to the left heat generating component 2d. Therefore, like the plurality of heat generating components 2c and 2d, the plurality of protrusions 20c and 20d are provided side by side in a direction orthogonal to the main flow direction F1.

[0074] Both of the plurality of protrusions 20c and 20d protrude from the opposing surface 16 toward the cooling surface 14. The right heat generating component 2c is on the protrusion center plane 22c of the right protrusion 20c, and the left heat generating component 2d is on the protrusion center plane 22d of the left protrusion 20d.

[0075] Also in the 14th embodiment described above, each of the plurality of protrusions 20c and 20d can form a secondary flow F2 that collides with a plurality of high-temperature portions 15c and 15d corresponding to the plurality of heat generating components 2c and 2d. That is, even when the plurality of heat generating components 2c and 2d are arranged in parallel, it is possible to cause the secondary flow F2 to collide with the high-temperature portions 15c and 15d of each of the plurality of heat generating components 2c and 2d, thereby improving the cooling performance.

[0076] (15th Embodiment) The 15th embodiment is provided with heat radiation fins 18 in the cooling container 10 with respect to the 1st embodiment, and since the other parts are the same as those of the 1st embodiment, only the parts different from the 1st embodiment will be described.

[0077] As shown in FIGS. 37 and 38, the heat exchanger 1 of the 15th embodiment includes a plurality of heat radiation fins 18 on the cooling surface 14. The plurality of heat radiation fins 18 are, for example, pin-shaped fins. The heat generated by the heat generating component 2 is directly absorbed by the refrigerant from the cooling surface 14 and is also transferred from the cooling surface 14 to the plurality of heat radiation fins 18 and absorbed by the refrigerant.

[0078] In the 15th embodiment described above, by combining the cooling of the heat-generating component 2 by the heat-radiating fins 18 and the cooling of the heat-generating component 2 by causing the secondary flow F2 of the refrigerant to collide with the high-temperature portion 15, the cooling performance for the heat-generating component 2 can be improved. Note that the shape of the heat-radiating fins 18 is not limited to a pin shape, and can be, for example, an arbitrary shape such as a plate shape. Also, the number of the heat-radiating fins 18 can be an arbitrary number.

[0079] (16th embodiment) The 16th embodiment is obtained by changing a part of the configuration of the cooling container 10 with respect to the 1st embodiment, and since the other parts are the same as those of the 1st embodiment, only the parts different from the 1st embodiment will be described.

[0080] As shown in FIGS. 39 and 40, the cooling container 10 included in the heat exchanger 1 of the 16th embodiment has an inclined passage 19 in a portion upstream of the protrusion 20. The inclined passage 19 is a passage that is inclined such that the main flow direction F1 of the refrigerant faces the cooling surface 14.

[0081] The refrigerant flowing through the inclined passage 19 in the main flow direction F1 has a velocity component toward the cooling surface 14. Therefore, the refrigerant flowing through the inclined passage 19 can, together with the secondary flow F2 formed by the protrusion 20, strengthen the collision force of the refrigerant against the high-temperature portion 15, and improve the cooling performance for the heat-generating component 2.

[0082] (17th to 19th embodiments) The 17th to 19th embodiments are obtained by adding a configuration for changing the flow passage cross-sectional area of the refrigerant flow passage 11 with respect to the 1st embodiment, and since the other parts are the same as those of the 1st embodiment, only the parts different from the 1st embodiment will be described.

[0083] (17th embodiment) The 17th embodiment will be described. As shown in Fig. 41, in the cooling container 10 of the heat exchanger 1 according to the 17th embodiment, the opposing surface 16 has an inclined surface 161 that is inclined so as to gradually approach the cooling surface 14 from the upstream side to the downstream side. Therefore, the distance between the opposing surface 16 and the cooling surface 14 gradually decreases from the upstream side to the downstream side of the refrigerant flow path 11. Accordingly, the flow path cross-sectional area of the refrigerant flow path 11 gradually becomes smaller from the upstream side to the downstream side. Note that the distance between the tip of the protrusion 21 and the cooling surface 14 is substantially constant from the upstream side to the downstream side.

[0084] The cooling container 10 included in the heat exchanger 1 according to the 17th embodiment described above has a shape in which the flow path cross-sectional area of the refrigerant flow path 11 gradually becomes smaller from the upstream side to the downstream side. Therefore, the flow velocity of the refrigerant flowing through the refrigerant flow path 11 gradually increases from the upstream side to the downstream side. Accordingly, the velocity boundary layer becomes thinner, heat transfer from the high-temperature part 15 to the refrigerant is promoted, and the cooling efficiency of the heat-generating component 2 can be improved.

[0085] (18th embodiment) The 18th embodiment will be described. As shown in Fig. 42, in the heat exchanger 1 according to the 18th embodiment as well, in the cooling container 10, the opposing surface 16 has an inclined surface 161 that is inclined so as to gradually approach the cooling surface 14 from the upstream side to the downstream side. Therefore, the distance between the opposing surface 16 and the cooling surface 14 gradually decreases from the upstream side to the downstream side of the refrigerant flow path 11. Accordingly, the flow path cross-sectional area of the refrigerant flow path 11 gradually becomes smaller from the upstream side to the downstream side. Note that the distance between the tip of the protrusion 21 and the cooling surface 14 also gradually decreases from the upstream side to the downstream side.

[0086] The heat exchanger 1 according to the 18th embodiment described above also exhibits the same operational effects as the 17th embodiment.

[0087] Although illustration is omitted, as a modification of the 17th and 18th embodiments, the cooling container 10 may have a shape in which the distance between the right side surface 17 and the left side surface 17 gradually approaches from the upstream side to the downstream side of the refrigerant flow path 11. Also with this configuration, the flow path cross-sectional area of the refrigerant flow path 11 can be gradually reduced from the upstream side to the downstream side, and the cooling efficiency of the heat-generating component 2 can be improved.

[0088] (19th Embodiment) The 19th embodiment will be described. As shown in FIGS. 43 to 45, in the 18th embodiment, the protrusion 20 has a shape in which the cross-sectional area perpendicular to the main flow direction F1 gradually increases from the upstream side to the downstream side of the refrigerant flow path 11. Specifically, the protrusion 20 has a shape in which the size in the width direction (that is, the distance between the left guide surface 24 and the right guide surface 24) gradually increases from the upstream side to the downstream side of the refrigerant flow path 11. Therefore, in the portion where the protrusion 20 is provided, the refrigerant flow path 11 has a gradually decreasing flow path cross-sectional area from the upstream side to the downstream side.

[0089] The heat exchanger 1 of the 19th embodiment described above also has a configuration in which the flow path cross-sectional area of the refrigerant flow path 11 gradually decreases from the upstream side to the downstream side. Therefore, the heat exchanger 1 of the 19th embodiment also exhibits the same operational effects as the 17th and 18th embodiments.

[0090] Although illustration is omitted, as a modification of the 19th embodiment, the protrusion 20 may have a shape in which the size in the height direction (that is, the distance between the tip portion 21 of the protrusion and the opposing surface 16) gradually increases from the upstream side to the downstream side of the refrigerant flow path 11. Also with this configuration, the flow path cross-sectional area of the refrigerant flow path 11 can be gradually reduced from the upstream side to the downstream side, and the cooling efficiency of the heat-generating component 2 can be improved.

[0091] (20th Embodiment) The 20th embodiment is different from the 1st embodiment in that a torsion plate 40 is provided in the cooling container 10, and since the other aspects are the same as those of the 1st embodiment, only the differences from the 1st embodiment will be described.

[0092] As shown in FIGS. 46 to 48, the heat exchanger 1 of the 20th embodiment includes a torsion plate 40 in the cooling container 10. The torsion plate 40 has a shape in which a plate-like member is twisted in the swirling direction of the secondary flow F2. The torsion plate 40 is also called a "torsion tape". The torsion plate 40 is disposed at an arbitrary position between the side surface 17 of the refrigerant container and the guide surface 24 of the protrusion 20, and between the cooling surface 14 and the opposing surface 16. Specifically, the torsion plate 40 is preferably disposed near the center of the swirling flow of the secondary flow F2. The torsion plate 40 is fixed to the inner wall of the cooling container 10 or the protrusion 20 by a fixing member (not shown).

[0093] In the 20th embodiment described above, due to the torsion plate 40 provided in the cooling container 10, the refrigerant flowing in the vicinity of the torsion plate 40 flows while swirling in a spiral shape. Therefore, the secondary flow F2 formed by the protrusion 20 is strengthened by the swirling flow formed by the torsion plate 40, so that the cooling performance for the heat generating component 2 can be improved.

[0094] (21st and 22nd embodiments) The 21st and 22nd embodiments are those in which the shape of the collision surface 23 of the protrusion 20 is changed with respect to the 1st embodiment, and since the other parts are the same as those in the 1st embodiment, only the parts different from the 1st embodiment will be described.

[0095] (21st embodiment) The 21st embodiment will be described. As shown in FIG. 49, in the heat exchanger 1 of the 21st embodiment, the collision surface 23 of the protrusion 20 is inclined with respect to the main flow direction F1. The angle θ4 formed between the collision surface 23 of the protrusion 20 and the opposing surface 16 is an acute angle (for example, 45°) on the downstream side. Note that the angle θ4 formed between the collision surface 23 of the protrusion 20 and the opposing surface 16 may be greater than 45° or less than 45°.

[0096] The heat exchanger 1 of the 21st embodiment can also achieve the same operational effects as those of the 1st embodiment. Further, in the heat exchanger 1 of the 21st embodiment, by making the angle θ4 formed between the collision surface 23 of the protrusion 20 and the opposing surface 16 an acute angle on the downstream side, the pressure loss of the refrigerant flowing through the refrigerant flow path 11 can be reduced.

[0097] (22nd Embodiment) The 22nd embodiment will be described. As shown in FIG. 50, in the heat exchanger 1 of the 22nd embodiment as well, the collision surface 23 of the protrusion 20 is inclined with respect to the main flow direction F1. The angle θ5 formed between the collision surface 23 of the protrusion 20 and the opposing surface 16 is an obtuse angle (for example, 135°) on the downstream side. Note that the angle θ5 formed between the collision surface 23 of the protrusion 20 and the opposing surface 16 may be greater than 135° or may be less than 135°.

[0098] The heat exchanger 1 of the 22nd embodiment can also achieve the same operational effects as those of the 1st embodiment. Further, in the heat exchanger 1 of the 22nd embodiment, by making the angle formed between the collision surface 23 of the protrusion 20 and the opposing surface 16 an obtuse angle on the downstream side, the pressure loss of the refrigerant flowing through the refrigerant flow path 11 can be reduced.

[0099] (Other Embodiments) In each of the above embodiments, the heat exchanger 1 used in the boiling cooling system 3 has been described. However, the present invention is not limited thereto. For example, the heat exchanger 1 may be used in a cooling system in which the boiling point of the refrigerant is set to a temperature higher than the average temperature during the operation of the heat generating component 2.

[0100] The present disclosure is not limited to the above-described embodiments, and can be appropriately modified within the scope described in the claims. Also, the above embodiments and parts thereof are not unrelated to each other, and can be appropriately combined except in cases where the combination is clearly impossible. Further, in the above embodiments, the elements constituting the embodiments are not necessarily essential except in cases where it is clearly stated as essential or where it is considered to be clearly essential in principle. Also, in the above embodiments, when numerical values such as the number, numerical value, quantity, range, etc. of the components of the embodiments are mentioned, they are not limited to that specific number except in cases where it is clearly stated as essential or where it is clearly limited to a specific number in principle. Also, in the above embodiments, when referring to the shape, positional relationship, etc. of the components, etc., they are not limited to that shape, positional relationship, etc. except in cases where it is clearly stated or where it is clearly limited to a specific shape, positional relationship, etc. in principle.

Explanation of Reference Numerals

[0101] 1 Heat exchanger 2 Heat-generating component 10 Cooling container 11 Refrigerant flow path 12 Refrigerant inlet 13 Refrigerant outlet 14 Cooling surface 20 Protrusion 23 Collision surface 24 Guide surface

Claims

1. A heat exchanger that performs heat exchange between a heat-generating component (2) and a refrigerant, comprising: a cooling container (10) that is integrally formed with or is a separate member from the heat-generating component and has a refrigerant flow path (11) through which the refrigerant flows from a refrigerant inlet (12) side to a refrigerant outlet (13) side; and protrusions (20) provided on the other surfaces (16, 17) of the inner wall of the cooling container, which are different from the cooling surface (14) on the side where the heat-generating component is disposed. The protrusion is: provided facing the main flow direction (F1) from the refrigerant inlet side to the refrigerant outlet side, and has a collision surface (23) against which the refrigerant flowing in the main flow direction collides; and a guide surface (24) that extends from the outer edge of the collision surface to the downstream side in the main flow direction and guides the secondary flow (F2) of the refrigerant formed by the collision at the collision surface toward a portion (15) directly below the heat-generating component on the cooling surface. The heat exchanger.

2. The heat exchanger according to claim 1, wherein the protrusion has a shape that gradually becomes thinner as it moves away from the portion of the other surface where the protrusion is provided.

3. The heat exchanger according to claim 1 or 2, wherein the guide surface is curved.

4. The heat exchanger according to claim 1 or 2, wherein the guide surface has fine unevenness grooves (30) formed by a plurality of fine unevenness extending in a direction intersecting the main flow direction.

5. The heat exchanger according to claim 1 or 2, wherein the cooling surface has fine unevenness grooves formed by a plurality of fine unevenness extending in a direction intersecting the main flow direction.

6. The heat exchanger according to claim 1 or 2, wherein the other surface has fine unevenness grooves formed by a plurality of fine unevenness extending in a direction intersecting the main flow direction.

7. Both the guide surface and the cooling surface have fine unevenness grooves formed by a plurality of fine unevenness extending in a direction intersecting the main flow direction, and the pitch of the unevenness forming the fine unevenness grooves of the guide surface and the pitch of the unevenness forming the fine unevenness grooves of the cooling surface are the same or an integral multiple. The heat exchanger according to claim 1 or 2.

8. At least one of the guide surface, the cooling surface, and the other surface has fine unevenness grooves formed by a plurality of fine unevenness extending in a direction intersecting the main flow direction, and the pitch and cross-sectional shape of the unevenness forming the fine unevenness grooves are designed according to physical properties including the kinematic viscosity coefficient of the refrigerant and the flow velocity. The heat exchanger according to claim 1 or 2.

9. The protrusion is provided on at least one of the opposing surface (16) of the other surface that faces the cooling surface and the side surface (17) of the other surface that faces in a direction perpendicular to the direction in which the opposing surface and the cooling surface face each other. The heat exchanger according to claim 1 or 2.

10. The protrusion is provided on the opposing surface of the other surface that faces the cooling surface. The heat exchanger according to claim 1 or 2.

11. On a virtual plane (22) connecting the tip (21) of the protrusion, which is the farthest from the part of the other surface where the protrusion is provided, and the center of the part of the other surface where the protrusion is provided, there is a part directly below the heat-generating component on the cooling surface. The heat exchanger according to claim 1 or 2.

12. A plurality of the protrusions (20a to 20d) are arranged at positions corresponding to a plurality of the heat-generating components (2a to 2d). The heat exchanger according to claim 1 or 2.

13. A plurality of the protrusions (20c, 20d) are arranged for one heat-generating component. The heat exchanger according to claim 1 or 2.

14. The heat exchanger according to claim 1 or 2, further comprising heat-radiating fins (18) provided on the cooling surface.

15. The cooling container has an inclined passage (19) inclined at a part upstream of the protrusion so that the main flow direction of the refrigerant faces the cooling surface. The heat exchanger according to claim 1 or 2.

16. The cooling container has a shape in which the cross-sectional area of the refrigerant flow path gradually decreases from the upstream side to the downstream side. The heat exchanger according to claim 1 or 2.

17. The cooling container has a shape in which the distance between the opposing surface of the other surface that faces the cooling surface and the cooling surface gradually approaches from the upstream side to the downstream side of the refrigerant flow path, and the cross-sectional area of the refrigerant flow path gradually decreases from the upstream side to the downstream side. The heat exchanger according to claim 1 or 2.

18. The protrusion has a shape in which the cross-sectional area perpendicular to the main flow direction gradually increases from the upstream side to the downstream side of the refrigerant flow path, The refrigerant flow path has a cross-sectional area that gradually decreases from the upstream side to the downstream side at the part where the protrusion is provided. The heat exchanger according to claim 1 or 2.

19. The heat exchanger according to claim 1 or 2, further comprising a torsion plate (40) provided in the refrigerant flow path, the torsion plate having a shape twisted in the turning direction of the secondary flow guided by the guiding surface.

20. The angle formed by the collision surface and the main flow direction is an arbitrary angle between 45° and 135°. The heat exchanger according to claim 1 or 2.

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