JP2005252092A - Heatsink - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To obtain a heatsink which can have sufficient cooling performance even for a heating body with large heat value, and perform epoch-making reduction of deterioration in cooling performance due to clogging of a refrigerant flow passage with foreign matter in a refrigerant. <P>SOLUTION: In the heatsink provided with the refrigerant flow passage 2 extending nearby a part where a heating body 3 is mounted in a heatsink main body 1 mounted with the heating body 3, a heat exchange plate 5 extending along a flow of the refrigerant nearby the part where the heating body 3 is mounted is arranged in the refrigerant flow passage 2 while being coupled with a container 1 in one body. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a heat sink for cooling a heating element such as a semiconductor element, and more particularly to a heat sink using a refrigerant.

  As a conventional heat sink of this type, in order to enhance the cooling performance for a heating element such as a semiconductor element, three flat copper members (hereinafter referred to as planar members) are overlapped to obtain an intermediate planar member and a lower planar surface. A plurality of inflow water passages are formed between the intermediate planar member and the upper planar member, and the inflow water passage and the outflow water channel are communicated with one end of the intermediate planar member. The water supply holes having a small hole diameter are provided in a row, and the heating element is mounted on top of the upper planar member on the water conveyance hole side, and a coolant such as water supplied to the inflow water channel is supplied to the upper planar member. The thing which intended the effective cooling of the said heat generating body by making it spray on a heat generating body mounting wall part is already known (for example, refer patent document 1).

Japanese Patent Laying-Open No. 2003-273441 (pages 5-6, FIG. 3)

  Since the conventional heat sink is configured as described above, the heat dissipation area in the cooling zone of the heating element is greatly suppressed by the plurality of small-diameter water guide holes provided in the intermediate plane member, and the heat dissipation area is sufficiently secured. Therefore, there is a problem that sufficient cooling performance cannot be obtained for a heating element having a higher calorific value. In addition, since the foreign material in the refrigerant passing through the small-diameter water guide hole is easily clogged, the water guide hole clogged with the foreign material is blocked and the refrigerant does not flow, resulting in a decrease in the refrigerant flow rate. There was a problem that the cooling performance deteriorated significantly.

  The present invention has been made to solve the above-described problems, and even if a heating element having a high calorific value is mounted, a sufficient heat radiation area for the refrigerant flowing through the refrigerant flow path can be obtained and the cooling performance can be obtained. An object of the present invention is to obtain a highly reliable heat sink that can greatly improve the temperature.

  The heat sink according to the present invention is a heat sink in which a refrigerant flow path that passes through the vicinity of the mounting portion of the heating element is provided inside the heat sink body in which the heating element is mounted, and the heating element is mounted inside the refrigerant flow path. A heat exchanging plate extending in the refrigerant flow direction in the vicinity of the portion is integrally coupled to the wall portion of the heat sink body.

  According to this invention, the heat exchange plate extending along the flow direction of the refrigerant in the vicinity of the mounting portion of the heat generating body in the heat sink main body is provided in the refrigerant flow path provided in the heat sink main body with the wall portion of the heat sink main body. Since it is configured to be integrally coupled, the heat transferred from the heating element to the heat sink body can be efficiently conducted to the heat exchange plate integrally coupled to the heat sink body in the vicinity of the heating element mounting portion of the heat sink body. For this reason, the heat radiation area for the refrigerant flowing in the vicinity of the heating element mounting portion of the heat sink body is increased by the heat exchange plate, and the heat exchange plate is always immersed in the refrigerant flowing through the refrigerant flow path. There is an effect that cooling efficiency is greatly improved by performing efficient heat exchange.

Embodiment 1 FIG.
1 is a cross-sectional plan view showing a main part of a heat sink according to Embodiment 1 of the present invention, and FIG. 2 is a longitudinal side view of FIG.
The heat sink shown in FIG. 1 and FIG. 2 includes a refrigerant flow path 2 formed inside a flat rectangular (specifically, flat rectangular) container 1 serving as a heat sink main body formed of a member having high thermal conductivity such as copper. And a heating element 3 such as a semiconductor element mounted on the upper wall surface of the container 1 on the front wall (hereinafter referred to as the front wall of the heat sink) 1a. In the illustrated example, the refrigerant flow path 2 is formed by integrally fitting and coupling the flow path defining member 4 in the container 1, so that the side wall surface of the flow path defining member 4 and the inner wall surface of the container 1 are interposed. More specifically, the refrigerant inlet side flow path (hereinafter referred to as inlet side refrigerant flow path) 2a along the inner surface of one side wall of the container 1 and the inner surface of the other side wall of the container 1 are described in more detail. The refrigerant outlet side flow path (hereinafter referred to as the outlet side refrigerant flow path) 2c and the inlet side refrigerant flow path 3a and the outlet side refrigerant flow along the front wall 1a in the vicinity of the mounting area of the heating element 3 in the container 1 The relay refrigerant flow path 2b connects the path 3c in series.

  In the refrigerant flow path 2 having such a flow path structure, a plurality of heat exchange plates 5 along the flow direction of the refrigerant flow in the relay refrigerant flow path 2b passing through the vicinity of the mounting region of the heating element 3 of the container 1. They are arranged in parallel in the road width direction at predetermined intervals. These heat exchange plates 5 are made of perforated flat plates having the same dimensions and provided with a plurality of refrigerant through holes 5a penetrating each heat exchange plate 5 in the thickness direction. The upper and lower wall surfaces of the path 2b are integrally coupled. Such a heat exchange plate 5 is formed of a member having a high thermal conductivity such as copper as in the case of the material of the container 1. However, any material can be used as long as it has a high thermal conductivity and is not easily corroded by the refrigerant. Such a material may be used.

FIG. 3 is a perspective view for explaining the dimensions and arrangement intervals of the heat exchange plate 5. In FIG. 3, WL is the interval width between adjacent heat exchange plates 5, WF is the thickness of the heat exchange plate 5, HF is the height of the heat exchange plate 5, and d is the hole diameter of the refrigerant through hole 5a.
As the interval width WL of the heat exchange plate 5 arranged in the relay refrigerant flow path 2b of the refrigerant flow path 2 is narrower and the number of sheets is further increased, the cooling performance is improved. On the other hand, the flow resistance of the refrigerant is also increased.
Therefore, in the first embodiment, for example, when the dimension of the heating element 3 is 10 mm in length × 2 mm in width and the heating value of the heating element 3 is about 50 W, the thickness WF of the heat exchange plate 5 is set to 0. It is preferable that the number of heat exchange plates 5 is 10 or less and the interval width WL between adjacent heat exchange plates 5 is about 0.1 to 1.0 mm. Further, it is most efficient to make the hole diameter d of the refrigerant passage hole 5a about 2 to 3 times the interval width WL between the adjacent heat exchange plates 5. Further, the number of refrigerant through holes 5a is such that the total opening area of the refrigerant through holes 5a in one heat exchange plate 5 is approximately equal to the interval width WL × height HF = area between adjacent heat exchange plates 5. It is preferable to set to.
In addition, the dimension, arrangement | positioning space | interval, etc. of the heat exchange plate 5 mentioned above were only illustrated in order to acquire ideal cooling performance, and are not necessarily specified as mentioned above.

Next, the operation will be described.
FIG. 4 is an operation explanatory view showing the flow of heat in the vicinity of the mounting portion of the heating element 3 in the container 1 as the heat sink main body with dotted arrows, and FIG. 5 is the solid arrow showing the flow of refrigerant between the plurality of heat exchange plates 5. It is operation | movement explanatory drawing shown by.
The heat generated by the heating element 3 is conducted to the upper wall (heat sink upper wall) of the container 1 and the heat sink front wall 1a as shown by the dotted arrows in FIG. Each of the heat exchange plates 5 arranged in 2b is conducted to the heat exchange plate 5 and radiated from the entire surface of the heat exchange plates 5 to the refrigerant in the relay refrigerant flow path 2b, so that heat is efficiently exchanged with the refrigerant. The Here, the refrigerant such as water flowing in the refrigerant flow path 2 flows from the inlet side refrigerant flow path 2a through the relay refrigerant flow path 2b to the outlet side refrigerant flow path 2c as shown by arrows in FIG. However, in the flow, the foreign matter S contained in the refrigerant flowing into the relay refrigerant flow path 2b from the inlet-side refrigerant flow path 2a is, as shown in FIG. 5, the flow path width in the relay refrigerant flow path 2b. It is also conceivable that the upstream end of the heat exchange plate 5 adjacent in the direction is clogged. Even in the case where the clogging occurs, each of the heat exchange plates 5 is provided with a plurality of refrigerant through holes 5a penetrating in the thickness direction, so that the heat exchange in which clogging with the foreign matter S has occurred. As shown by the arrows in FIG. 5, the refrigerant flowing in the refrigerant flow path adjacent to the refrigerant flow path between the plates 5 flows into the flow path between the heat exchange plates 5 where the clogging occurs. 5 from the refrigerant passage hole 5a. For this reason, the flow of the refrigerant can be maintained also in the flow path between the heat exchange plates 5 in which the clogging due to the foreign matter S has occurred.

  According to the first embodiment described above, in the refrigerant flow path 2 formed inside the container 1 serving as the heat sink body with the heating element 3 mounted on the upper wall surface, in the vicinity of the mounting region of the heating element 3 of the container 1. A plurality of heat exchanging plates 5 having a flat plate shape extending in a direction along the flow direction of the refrigerant and parallel to the width direction of the flow path at a predetermined interval in the relay refrigerant flow path 2b which is a refrigerant flow path passing through Since each upper and lower end portion is arranged so as to be integrally coupled with the wall portion of the container 1, the heat radiation area for the refrigerant in the refrigerant flow path 2 in the vicinity of the mounting portion of the heating element 3 in the container 1 is The heat exchanger plate 5 is remarkably increased by the plurality of heat exchange plates 5 and all of the heat exchange plates 5 are always immersed in the refrigerant flowing through the refrigerant flow path 2, so that the heat sink on which the heating element 3 having a high calorific value is mounted is mounted. Even It is possible to secure a sufficient heat radiation area in the refrigerant flow path in the place passing through the vicinity of the mounting portion of the heating element 3, thereby performing an effective heat exchange and greatly improving the cooling efficiency. is there.

  In particular, according to the first embodiment, since the plurality of refrigerant through holes 5a penetrating in the thickness direction are provided in the heat exchange plate 5, the refrigerant flow path between the heat exchange plates 5 is provided. Even when clogging due to foreign matter S in the refrigerant occurs in a certain relay refrigerant flow path 2b, the refrigerant flowing through the non-clogging relay refrigerant flow path 2b adjacent to the clogged relay refrigerant flow path 2b becomes the clogging side. The heat exchange plate 5 flows into the clogged relay refrigerant flow path 2b through the refrigerant passage hole 5a. For this reason, it is possible to minimize a decrease in refrigerant flow resistance in the clogged relay refrigerant flow path 2b, and furthermore, in the clogged relay refrigerant flow path 2b, the conduction heat of the heat exchange plate 5 is used as the refrigerant. Since heat can be dissipated, there is an effect that the deterioration of the cooling performance due to the clogging of the refrigerant flow path due to the foreign matter S in the refrigerant can be dramatically reduced.

  Further, according to the first embodiment, the hole diameter d of the refrigerant passage hole 5a of each heat exchange plate 5 is set to a size of about 2 to 3 times the interval width WL between the adjacent heat exchange plates 5. Since it comprised, there exists an effect that there is very little possibility that the said coolant through-hole 5a will be clogged with the foreign material S in a coolant. Furthermore, since the total opening area of the refrigerant through holes 5a in each heat exchange plate 5 is set to be approximately equal to the interval width WL × height HF = area between adjacent heat exchange plates 5, There is an effect that an increase in flow resistance of the refrigerant passing through the refrigerant passage hole 5a can be minimized. Further, each of the heat exchange plates 5 is parallel to the heat sink front wall 1a along the flow direction of the refrigerant in the relay refrigerant flow path 2b, and at a predetermined interval in the flow path width direction of the relay refrigerant flow path 2b. Since it is configured so as to be arranged adjacent to each other in parallel, the refrigerant rectifying effect in the relay refrigerant flow path 2b can be obtained, and the refrigerant flow distribution in the relay refrigerant flow path 2b can be made uniform. .

Embodiment 2. FIG.
FIG. 6 is a cross-sectional plan view showing the main part of the heat sink according to Embodiment 2 of the present invention. The same or corresponding parts as those in FIGS.
In the second embodiment, a plurality of heat exchange plates 5 arranged at predetermined parallel intervals in the relay refrigerant flow path 2b of the refrigerant flow path 2 are arranged in a direction along the refrigerant flow direction of the relay refrigerant flow path 2b. Are formed differently. That is, in the first embodiment, a plurality of heat exchange plates 5 each having the same size are arranged in parallel to the relay refrigerant flow path 5b. However, in the second embodiment, a plurality of heat exchange plates adjacent to each other. 5 is a heat exchange plate 51 whose length along the refrigerant flow direction in the relay refrigerant flow path 2b is longer than the width dimension of the flow path defining member 4, and more in the refrigerant flow direction than the heat exchange plate 51. The heat exchanging plate 52 is combined with a short heat exchanging plate 52, and the heat exchanging plates 51 and 52 are alternately arranged in parallel with the relay refrigerant flow path 2b.

  According to the second embodiment configured as described above, the same effect as in the first embodiment can be obtained, and the refrigerant from the inlet-side refrigerant flow path 2a can be obtained by the heat exchange plate 51 having a long length. Can be directed to the relay refrigerant flow path 2b between the adjacent heat exchange plates 5, and the refrigerant flowing through the relay refrigerant flow path 2b can be directed to the outlet-side refrigerant flow path 2c. In the second embodiment, the two heat exchange plates 51 and 52 having different lengths are illustrated as described above, and the heat exchange plate 51 having the longer length is arranged on the heat sink front wall 1a side, that is, the heating element. Although the three heat exchange plates 5 having different lengths are arranged so that the heat exchange plate having the longer length approaches the mounting portion side of the heating element 3 sequentially, The same effect can be obtained in this case.

FIG. 7 is a front view showing a modification of the heat exchange plate applied to the heat sink according to the first and second embodiments of the present invention, and FIG. 8 is a modification in which the arrangement of the refrigerant through holes of the heat exchange plate in FIG. FIG.
In the first and second embodiments, the refrigerant through hole 5a of the heat exchange plate 5 is a circular hole. However, the refrigerant through hole 5a may have a square hole shape and arrangement as shown in FIGS. In this case, the same effect as in the first and second embodiments can be obtained. In short, the refrigerant through hole 5a provided in the heat exchange plate 5 may have any shape and arrangement as long as the refrigerant can be divided into the refrigerant flow path between the adjacent heat exchange plates 5.

Embodiment 3 FIG.
FIG. 9 is a cross-sectional plan view showing the main part of the heat sink according to Embodiment 3 of the present invention.
In the third embodiment, the refrigerant passage hole 5a of the heat exchange plate 5 in the first and second embodiments is replaced with a cutout portion 5b provided in the height direction of the heat exchange plate 5, and the cutout portion 5b is replaced with a refrigerant. It is a through hole. Thus, according to the third embodiment in which the cutout portion 5b of the heat exchange plate 5 is used as the refrigerant passage hole, the same effect as that of the first embodiment can be obtained, and the refrigerant upstream of the adjacent heat exchange plate 5 can be obtained. When clogging due to foreign matter S occurs between the ends, a large amount of refrigerant flows into the clogged refrigerant flow path between the heat exchange plates 5 from the adjacent clogged refrigerant flow path by the notch 5b. Therefore, there is an effect that the deterioration of the cooling performance in the clogged refrigerant flow path can be further reduced.

Embodiment 4 FIG.
FIG. 10 is a longitudinal side view showing a main part of a heat sink according to Embodiment 4 of the present invention, and FIG. 11 is a cross-sectional plan view of FIG. 10. The same or corresponding parts as those in FIGS. Therefore, duplicate explanation is omitted.
In the first to third embodiments, the heat sink in which the refrigerant flow path 2 for flowing the refrigerant in the horizontal direction in the container 1 is described. However, in the fourth embodiment, the refrigerant flow path 2 is disposed inside the container 1. The space is divided up and down and the flow path configuration is such that the refrigerant flows from the lower space toward the upper space, and the details will be described below.
In the fourth embodiment, the internal space of the container 1 is divided up and down by a horizontal partition plate (flow path defining member) 4 integrally coupled to the container 1, so that the upper space is separated from the outlet side refrigerant flow. A path (upper refrigerant flow path) 2c and the lower space are partitioned and formed as an inlet side refrigerant flow path (lower refrigerant flow path) 2a, and an end of the partition plate 4 on the heat sink front wall 1a side (heating element 3 mounting direction) The relay refrigerant flow path 2b which connects the said inlet side refrigerant flow path 2a and the outlet side refrigerant flow path 2c is formed by notching a part. A plurality of heat exchange plates 5 rising in the vertical direction from the relay refrigerant flow path 2b made of the end notches of the partition plate 4 as described above are arranged in parallel at a predetermined interval. Here, the heat exchange plate 5 has an upper end on the upper wall of the container 1, one side end face on the front wall 1 a of the container 1, and a lower part on the other end face on the notch end face of the partition plate 4. It is integrally connected.

  In the above, the flow passage area of the relay refrigerant flow path 2b between the heat sink front wall 1a and the partition plate 4 is smaller than the cross-sectional area of the inlet side refrigerant flow path 2a in order to increase the flow rate of the refrigerant. Set. Here, since the height of the inlet side refrigerant flow path 2a is generally 5 mm or less, the flow width of the relay refrigerant flow path 2b between the heat sink front wall 1a and the partition plate 4 is 5 mm or less. This is preferable because the cooling efficiency is increased. Such a dimension setting is shown as a representative example for obtaining an ideal cooling performance. However, as long as the refrigerant collides with the lower surface of the mounting portion upper wall (heat sink upper wall) of the heating element 3 in the container 1. Since the same effect can be obtained, any size may be used.

Next, the operation will be described. FIG. 12 is an operation explanatory view showing the flow of heat from the heat generating element of the heat sink according to the fourth embodiment.
In the refrigerant flow path 2 in the container 1, the refrigerant passes through the relay refrigerant flow path 2 b between the inlet side refrigerant flow path 2 a at the lower part of the partition plate 4 and the heat exchange plate 5, as indicated by arrows in FIGS. 10 and 11. Then, after colliding with the lower surface of the upper wall of the heat sink in the mounting portion of the heating element 3, it flows to the outlet side refrigerant flow path 2c above the partition plate 4. In this state, the heat generated by the heating element 3 is conducted to the heat sink front wall 1a and the heat sink upper wall having high thermal conductivity as shown by the dotted arrows in FIG. The conducted heat is then conducted to the heat exchange plate 5 and then radiated from the entire surface of each heat exchange plate 5 to the refrigerant.

  According to the fourth embodiment described above, the refrigerant flow path 2 having a flow path configuration in which the refrigerant flows from the inlet side refrigerant flow path 2a at the lower part of the partition plate 4 toward the outlet side refrigerant flow path 2c at the upper part of the partition plate 4 is provided. In the heat sink provided, a relay refrigerant channel 2b is formed between the notched end of the partition plate 4 and the heat sink front wall 1a by cutting out the end portion of the partition plate 4, and rises from the relay refrigerant channel 2b. Since the plurality of heat exchange plates 5 are arranged in parallel, and the heat exchange plates 5 are integrally coupled to the heat sink front wall 1a, the heat sink upper wall, and the cut-out end portions of the partition plate 4, the heat generator 3 can be connected to the heat sink. The heat conducted to the front wall 1 a and the heat sink upper wall can be efficiently conducted to the plurality of heat exchange plates 5 in the refrigerant flow path 2. Since heat is radiated to the refrigerant in the refrigerant flow path 2, the heat radiation area to the refrigerant flowing through the refrigerant flow path 2 can be increased by the plurality of heat exchange plates 5, and good cooling performance can be obtained. There is.

  Further, in the fourth embodiment, the refrigerant that flows between the adjacent heat exchange plates 5 in the relay refrigerant flow path 2b from the inlet-side refrigerant flow path 2a at the lower part of the partition plate 4 is heated near the mounting portion of the heating element 3. A cooling effect by colliding with the lower surface of the upper wall is also obtained, and therefore, there is an effect that a better cooling performance can be obtained than in the case of the first embodiment. Furthermore, also in this fourth embodiment, each of the heat exchange plates 5 is provided with the same refrigerant passage hole 5a as in the first embodiment, so that the upstream end of adjacent heat exchange plates 5 is between When clogging occurs due to the foreign matter S in the refrigerant, the same epoch-making effect as in the first embodiment can be obtained.

Embodiment 5 FIG.
FIG. 13 is a longitudinal side view showing a main part of a heat sink according to Embodiment 5 of the present invention. The same parts as those in FIGS.
In the fifth embodiment, the heat exchange plate 5 according to the fourth embodiment is formed to be narrower than the notch width of the partition plate 4 (the flow width of the relay refrigerant flow channel 2b), and the upper end of the heat exchange plate 5 is formed. And the end edge of the heat exchange plate 5 on the side opposite to the heat sink front wall 1a are integrally coupled to the notched end of the partition plate 4, respectively. In the fifth embodiment configured as described above, the same effect as in the fourth embodiment can be obtained except that the heat exchange plate 5 is not coupled to the heat sink front wall 1a. Further, by separating the heat exchange plate 5 formed so as to be narrow from the heat sink front wall 1a, an increase in refrigerant flow resistance can be suppressed.

Embodiment 6 FIG.
FIG. 14 is a longitudinal side view showing a main part of a heat sink according to Embodiment 6 of the present invention. In this sixth embodiment, the heat exchange plate 5 formed in the same manner as in the fifth embodiment is turned sideways so as to be integrally coupled to the heat sink front wall 1a and the notch ends of the partition plate 4, and the heat exchange plate The upper end of 5 is configured to be separated from the upper wall of the heat sink. In the sixth embodiment configured as described above, the same effect as in the fourth embodiment can be obtained except that the upper end of the heat exchange plate 5 is separated from the upper wall of the heat sink. Further, as described above, the height of the heat exchange plate 5 is shortened by separating the upper end of the heat exchange plate 5 from the upper wall of the heat sink, so that an increase in refrigerant flow resistance can be suppressed.

Embodiment 7 FIG.
15 is a longitudinal side view showing the main part of the heat sink according to Embodiment 7 of the present invention, and FIG. 16 is a cross-sectional plan view of FIG. 15. The same or corresponding parts as those in FIGS. Therefore, duplicate explanation is omitted.
In the seventh embodiment, the refrigerant passage hole 5a of the heat exchange plate 5 in the fourth embodiment is eliminated, the wide heat exchange plate 53 without the refrigerant passage hole 5a, and the width without the refrigerant passage hole 5a as well. By combining with the narrow heat exchange plate 54, the wide heat exchange plate 53 is integrally coupled to the heat sink front wall 1a, and the narrow heat exchange plate 54 is integrally coupled to the notch end portion of the partition plate 4, so that a plurality of The wide heat exchange plate 53 and the narrow heat exchange plate 54 are alternately arranged in parallel at a predetermined interval, and the wide heat exchange plate 53 and the narrow heat exchange plate 54 have different heights. It is composed. According to the seventh embodiment having such a configuration, even if all the heat exchange plates 53 and 54 do not have a refrigerant through hole, the inlet of the lower part of the partition plate 4 is provided in the flow path between the adjacent heat exchange plates 53 and 54. The refrigerant can be introduced from the side refrigerant flow path 2a and can be flowed to the outlet side refrigerant flow path 2c at the upper part of the partition plate 4, and the substantially same effect as in the first embodiment can be obtained.

It is a cross-sectional top view which shows the principal part of the heat sink by Embodiment 1 of this invention. It is a vertical side view of FIG. It is a perspective view for demonstrating the dimensional relationship of the heat exchange plate shown by FIG. 1 and FIG. It is operation | movement explanatory drawing which shows the heat flow in the heat generating body mounting part vicinity of the heat sink by Embodiment 1 of this invention. It is operation | movement explanatory drawing for demonstrating the flow of the refrigerant | coolant in the principal part of the heat sink by Embodiment 1 of this invention. It is a cross-sectional top view which shows the principal part of the heat sink by Embodiment 2 of this invention. It is a front view which shows the modification of the heat exchange plate applied to the heat sink by Embodiment 1, 2 of this invention. It is a front view which shows the modification of FIG. It is a cross-sectional plan view which shows the principal part of the heat sink by Embodiment 3 of this invention. It is a vertical side view which shows the principal part of the heat sink by Embodiment 4 of this invention. It is a cross-sectional plan view of FIG. It is operation | movement explanatory drawing of the heat sink by Embodiment 4 of this invention. It is a vertical side view which shows the principal part of the heat sink by Embodiment 5 of this invention. It is a vertical side view which shows the principal part of the heat sink by Embodiment 6 of this invention. It is a vertical side view which shows the principal part of the heat sink by Embodiment 7 of this invention. FIG. 16 is a transverse plan view of FIG. 15.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Container (heat sink main body), 1a Heat sink front wall, 2 Refrigerant flow path, 2a Inlet side refrigerant flow path, 2b Relay refrigerant flow path, 2c Outlet side refrigerant flow path, 3 Heat generating body, 4 Flow path defining member, 5 Heat Exchange plate, 5a Refrigerant through hole, 5b Notch, 51-54 Wide heat exchange plate, S foreign matter.

Claims (5)

  In a heat sink in which a refrigerant flow path passing through the vicinity of the mounting portion of the heating element is provided inside the heat sink body in which the heating element is mounted, the flow of the refrigerant in the vicinity of the mounting portion of the heating element in the refrigerant flow path. A heat sink, characterized in that a heat exchange plate extending along a direction is integrally coupled to a wall portion of the heat sink body.   The heat sink according to claim 1, wherein a plurality of the heat exchange plates are arranged at predetermined parallel intervals in the width direction of the refrigerant flow path.   The heat sink according to claim 1 or 2, wherein the heat exchange plate is provided with a refrigerant through hole penetrating in a thickness direction thereof.   4. The heat sink according to claim 3, wherein a plurality of the refrigerant through holes are provided on one heat exchange plate.   The refrigerant flow path is divided and formed into an upper refrigerant flow path and a lower refrigerant flow path by a flow path defining member that divides the internal space of the heat sink body up and down. The flow path defining member includes the upper refrigerant flow path. The heat sink according to claim 1, wherein a notch portion that communicates with the lower refrigerant flow path is provided, and a heat exchange plate is disposed in the notch portion.

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