JP6529324B2 - Heat exchanger - Google Patents

Description

  The present invention relates to a heat exchanger that cools a heat generating element such as a semiconductor.

  Semiconductor devices, such as IGBT (Insulated Gate Bipolar Transistor) and a diode, are integrated in power converters, such as an inverter and a converter. These semiconductor elements are usually mounted on a circuit board formed by bonding metal foils on both sides of a ceramic plate from the viewpoint of cooling capacity.

  A power converter includes a heat exchanger for efficiently cooling a semiconductor element, and a circuit board is often soldered to the outer surface of the heat exchanger. For example, Patent Document 1 discloses an aluminum heat sink. The main body of the heat sink has a hollow portion, and an inner fin for improving the cooling capacity is provided in the hollow portion. In addition, on the surface of the heat sink body, a thermally conductive insulating substrate on which electronic components such as semiconductor elements are mounted is soldered.

JP 2008-166356 A

  In recent years, the calorific value of the semiconductor element has been increased along with the increase in output of the power conversion device. Therefore, in order to perform cooling of the semiconductor element efficiently, it is strongly required to significantly improve the performance of the heat exchanger as compared to the prior art.

  For example, in order to improve the cooling capacity of the heat exchanger, it is effective to widen the contact area between the inner fins and the refrigerant. However, when the contact area between the inner fin and the refrigerant is increased, the cross-sectional area of the refrigerant flow path in the inner fin becomes narrow, and there is a problem that the pressure loss when flowing the refrigerant into the heat exchanger becomes large.

  Further, also in a high-power power converter, it is required to secure a life characteristic equal to or more than that of the conventional one. However, since the ceramic plate of the circuit board has a linear expansion coefficient significantly different from that of the aluminum member that constitutes the heat exchanger, the thermal stress according to the difference in the linear expansion coefficient with the aluminum member during use of the power conversion device, etc. It occurs on ceramic plates. When the calorific value of the semiconductor element is increased, the temperature change of the aluminum member or the ceramic plate is increased, and as a result, the thermal stress applied to the ceramic plate is increased. Therefore, when the conventional heat exchanger is applied to a high-power power conversion device, there is a problem that a crack or the like is easily generated in the ceramic plate of the circuit board.

  The present invention has been made in view of the above background, and an object of the present invention is to provide a heat exchanger which has excellent performance and can make the life characteristic of the power converter equal to or more than that of the prior art.

One aspect of the present invention is a heat exchanger comprising an aluminum member, wherein
It is formed between a top wall having a heating element mounting surface on which the heating element is mounted on the outer surface, a bottom wall disposed facing the top wall, and the top wall and the bottom wall. A main body having an inner space,
One or more dividers that divide the internal space into layers;
A three- layered space defined by the partition plate and aligned in the opposing direction of the top wall and the bottom wall;
A heat sink disposed in each of the above-mentioned layered spaces, through which a refrigerant flows ;
A communication passage for communicating the adjacent layered spaces;
A supply header portion in communication with the first layer facing the top wall portion among the three- layered space;
And a discharge header portion communicating with the final layer facing the bottom wall portion among the three layers of the layered space,
The first heat sink disposed in the first layer is joined to both the top wall and the first partition plate which is the partition plate facing the first layer,
The final heat sink disposed in the final layer is joined to either the bottom wall portion or the partition plate facing the final layer, and has a gap between the other and the other,
A second layer provided with a second heat sink is provided between the first layer and the final layer,
The second heat sink is disposed between the first heat sink and the final heat sink in the opposing direction of the top wall and the bottom wall, and faces the first partition plate and the final layer. It is joined to both sides of the second partition which is a board,
The communication passage for communicating the first layer and the second layer is disposed downstream of the first heat sink in the refrigerant flow path,
The heat exchanger is characterized in that the communication passage communicating the second layer and the final layer is disposed downstream of the second heat sink in the refrigerant flow path .

  The heat exchanger has a plurality of the layered spaces divided by the partition plate, and the adjacent layered spaces communicate with each other by the communication path provided in the partition plate. The heat exchanger can suppress an increase in pressure loss when the refrigerant flows by dividing the inner space of the main body into layers.

  Further, the heat sinks are disposed in the respective layered spaces. Therefore, the heat exchanger has a high cooling capacity.

  Further, the final heat sink is fixed to either one of the bottom wall portion or the partition plate facing the final layer, and has a gap between the other and the other. As a result, the heat exchanger can easily prevent the rigidity from becoming excessively high. And, as a result of the heat exchanger being able to easily avoid that the rigidity becomes excessively high, for example, a circuit board having a ceramic plate and a metal foil or metal plate joined to both sides of the ceramic plate; When a heating element having a semiconductor element mounted on a metal foil is mounted on the heating element mounting surface, the thermal stress applied to the ceramic plate can be easily reduced. So, the said heat exchanger can suppress that a crack etc. generate | occur | produce in a ceramic board.

  As described above, the heat exchanger has excellent performance and can improve the life characteristics of the power converter.

FIG. 2 is a perspective view of a heat exchanger in Embodiment 1; The components expanded view of FIG. FIG. 2 is a top view of a heat exchanger in Embodiment 1. 5 is a bottom view of the heat exchanger in Embodiment 1. FIG. V-V arrow directional cross-sectional view of FIG. VI-VI arrow sectional drawing of FIG. VII-VII arrow sectional drawing of FIG. VIII-VIII sectional view taken on the line in FIG. FIG. 3A is a plan view of the first plate of the laminated heat sink, FIG. 2B is a plan view of the second plate, and FIG. 2C is a plan view of the state in which the first plate and the second plate are superimposed. FIG. 10 is an enlarged cross-sectional view showing the main parts of a heat exchanger in which a pin fin type heat sink is adopted as a final heat sink in the first modification; The perspective view of the last heat sink in modification 1. FIG. FIG. 13 is an enlarged perspective view showing the main part of a heat exchanger in which a corrugated fin type heat sink is adopted as a final heat sink in the second modification example. (A) Top view of 1st plate of laminated heat sink which has a rectangular-shaped opening part in modification 3 A top view of the 2nd plate (b). FIG. 16 is a perspective view of a model E1 in the second embodiment. FIG. 16 is a component development view of a model E1 in the second embodiment. XVI-XVI arrow sectional drawing of FIG. XVII-XVII arrow sectional drawing of FIG. The XVIII-XVIII line arrow sectional view of FIG. The XIX-XIX line arrow directional cross-sectional view of FIG. (A) top view of 1st plate of laminated heat sink, (b) top view of 2nd plate, (c) enlarged plan view near the opening of the 1st plate in model E1. FIG. 16 is a component development view of a model C1 having a layered space of one layer in Example 2. FIG. 17 is a cross-sectional view corresponding to FIG. 16 in a model C1. The XXIII-XXIII line arrow sectional view of FIG. FIG. 16 is a component development view of a model C2 having two-layered space in Example 2. FIG. 17 is a cross-sectional view corresponding to FIG. 16 in a model C2; XXVI-XXVI arrow sectional drawing of FIG. XXVII-XXVII sectional view taken on the line in FIG. FIG. 17 is a cross-sectional view corresponding to FIG. 16 of a model C3 having a three-layered layered space in which the final heat sink and the partition plate are in contact in Example 2; FIG. 14 is an explanatory view showing the result of thermal analysis in Example 2; FIG. 14 is an explanatory view showing a result of distortion analysis in Example 2;

  As used herein, the term "joining" is used not only when parts separately prepared are joined metallurgically, but also when they are joined mechanically and when they are adhered. . Metallurgical bonding is most preferable from the viewpoint of improving heat conductivity and thermal efficiency. As metallurgical bonding, specifically, methods such as welding, pressure welding, brazing, soldering, diffusion bonding and the like can be adopted. When brazing or diffusion bonding is performed, brazing or the like may be performed after metalizing the bonding surface in advance. Also, as metallurgical bonding, it is possible to adopt a method of direct bonding using an active metal. In the case of joining members by adhesion, an inorganic adhesive is usually used from the viewpoint of heat resistance.

  The aluminum member which comprises the said heat exchanger is comprised from pure aluminum or conventionally well-known aluminum alloy. The material of the aluminum member can be appropriately selected from pure aluminum or a conventionally known aluminum alloy according to the cooling capacity, heat resistance, rigidity and the like required for the heat exchanger.

  The heat exchanger has a second heat generating body mounting surface for mounting the heat generating body on the outer surface of the bottom wall portion, the final heat sink is fixed to the bottom wall portion, and the final heat sink A gap may be present between the partition plate facing the final layer.

  In the conventional heat exchanger having no gap between the final heat sink and the partition plate, the heat from the heating element mounted on the top wall is easily transferred to the bottom wall and the final heat sink. On the other hand, in the heat exchanger, since the gap is present, the heat transfer from the heating element mounted on the top wall to the bottom wall and the final heat sink can be reduced as compared to the prior art.

  Therefore, the heat exchanger can sufficiently cool the heating element at each of the heating element mounting surface of the top wall and the second heating element mounting surface of the bottom wall. And the heat exchanger comprised in this way cools more heating elements more, without increasing the volume of a heat exchanger compared with the case where it does not have a 2nd heat generating body mounting surface in a bottom wall part. be able to.

  The internal space is divided into three layers of the layer space by the partition plate, and a second heat sink is disposed in the second layer adjacent to the first layer, and the second heat sink is the first layer. It is preferable to be joined to both the side partition plate and the second layer side partition plate. In this case, the heat exchanger can diffuse the heat of the heating element mounted on the top wall to both the partition plate on the first layer side and the partition plate on the second layer side. As a result, it is possible to further improve the cooling capacity of the heating element mounting surface of the top wall.

  Further, in the case where the heat exchanger is configured such that the heat generating element can be mounted on both the outer surface and the bottom wall of the top wall, the inner space is divided into three layers to obtain the bottom wall. The cooling capacity of the second heat generator mounting surface can be made sufficiently high.

  It is preferable that the first heat sink and the second heat sink have a refrigerant flow path in which a plurality of plates having a large number of openings are stacked and the openings of adjacent plates communicate with each other. That is, it is preferable that the first heat sink and the second heat sink be a laminated heat sink composed of a plurality of the plates.

  The heat exchanger is configured such that the refrigerant flows from the first layer to the final layer. Therefore, the temperature of the refrigerant flowing through the inside of the first heat sink and the second heat sink is lower than the temperature of the refrigerant flowing through the inside of the final heat sink. Therefore, the heat exchanger can more effectively improve the cooling ability on the heating element mounting surface of the top wall by adopting the laminated heat sink having high cooling ability as the first heat sink and the second heat sink. it can.

  In the laminated heat sink employed in the first heat sink and the second heat sink, the width dimension obtained by measuring in the flow direction of the refrigerant in the state of being disposed in the layered space is the length obtained by measuring in the direction perpendicular to the flow direction It is preferred to be shorter than the dimensions. The laminated heat sink has an excellent cooling capacity because it is easy to widen the contact area with the refrigerant as compared with a heat sink having plate fins or pin fins. However, since the laminated heat sink tends to narrow the cross-sectional area of the flow path in the heat sink, there is a problem that the pressure loss of the heat exchanger tends to be high.

  On the other hand, in the heat exchanger, the contact area between the heat sink and the refrigerant is sufficiently secured by specifying the dimensions and the arrangement of the laminated heat sinks adopted for the first heat sink and the second heat sink as described above. The flow path length of the refrigerant flowing in the heat sink can be easily shortened. As a result, the heat exchanger can further reduce pressure loss.

  The final heat sink preferably has a flat base portion and a large number of fins erected from the base portion. That is, the final heat sink is preferably a fin heat sink. In this case, it is possible to further reduce the pressure loss when flowing the refrigerant through the heat exchanger. As the fins, fins of known shapes such as plate fins, pin fins and corrugated fins can be employed.

Example 1
An embodiment of the heat exchanger 1 will be described with reference to the drawings. The heat exchanger 1 is made of an aluminum member, and as shown in FIGS. 1, 5, 6 and 8, the main body 2 having the top wall 21 and the bottom wall 22 and one or more partitions A plate 3 (3a, 3b), a plurality of layered spaces 4 (4a, 4b, 4c), a plurality of heat sinks 5 (5a, 5b, 5c), a supply header portion 11, and a discharge header portion 12 ing. As shown in FIGS. 1 and 3, the top wall 21 has a heating element mounting surface 13 on which the heating element is mounted on the outer surface. As shown in FIGS. 2 and 5, the bottom wall portion 22 is disposed to face the top wall portion 21, and an internal space 200 is formed between the top wall portion 21 and the bottom wall portion 22.

  As shown in FIG. 5, the partition plate 3 divides the internal space 200 of the main body 2. The plurality of layered spaces 4 partitioned into layers by the partition plate 3 are arranged in the opposing direction of the top wall 21 and the bottom wall 22. Further, the layered spaces 4 adjacent to each other are in communication by the communication passages 41 (41a, 41b). A heat sink 5 (5a, 5b, 5c) is disposed in each layered space 4.

  As shown in FIG. 6, the supply header portion 11 communicates with the first layer 4 a facing the top wall portion 21 among the plurality of layered spaces 4. As shown in FIG. 8, the discharge header portion 12 is in communication with the final layer 4 c facing the bottom wall portion 22 among the plurality of layered spaces 4. As shown in FIG. 5, the first heat sink 5a disposed in the first layer 4a is joined to both the top wall portion 21 and the partition plate 3a facing the first layer 4a. Further, the final heat sink 5c disposed in the final layer 4c is joined to either one of the bottom wall portion 22 or the partition plate 3b facing the final layer 4c, and there is a gap 42 with the other. ing. Hereinafter, the heat exchanger 1 of this example will be described in detail.

  As shown in FIG. 1, the heat exchanger 1 of this example has a substantially rectangular parallelepiped main body 2. The refrigerant supply pipe 14 for supplying the refrigerant to the supply header portion 11 is disposed on one end side in the longitudinal direction of the main body portion 2, and the refrigerant discharge pipe 15 for discharging the refrigerant from the discharge header portion 12 is disposed on the other end side. It is done.

  In this example, the longitudinal direction of the main body 2 may be referred to as “longitudinal direction X”, the refrigerant supply pipe 14 side in the longitudinal direction X may be referred to as “front X1”, and the refrigerant discharge pipe 15 side may be referred to as “rear X2”. The direction in which the top wall 21 and the bottom wall 22 are arranged is referred to as "height direction Z", the side of the top wall 21 in the height direction Z is referred to as "upper Z1", and the side of the bottom wall 22 is " There is a thing called lower part Z2. In addition, a direction orthogonal to both the longitudinal direction X and the height direction Z may be referred to as “horizontal direction Y”. The indication about these directions is for convenience, and has nothing to do with the actual direction when using the heat exchanger 1.

  As shown in FIG. 3, the top wall 21 of the present example has a rectangular shape when viewed from the height direction Z. The top wall portion 21 has a heating element mounting surface 13 (hereinafter, the heating element mounting surface 13 of the top wall portion 21 will be referred to as a "first heating element mounting surface 131") on its outer surface. On the first heating element mounting surface 131, for example, a heating element such as a circuit board on which a switching element such as an IGBT is mounted can be mounted. These heat generating elements can be mounted, for example, in a region corresponding to the upper portion Z1 of the first heat sink 5a.

  As shown in FIG. 4, the bottom wall 22 of the present example has substantially the same shape as the top wall 21. The bottom wall portion 22 has notches 221 and 222 at both ends in the longitudinal direction X. A refrigerant supply pipe 14 is attached to a notch 221 provided in the front X1 in the longitudinal direction X. In addition, a refrigerant discharge pipe 15 is attached to a notch 222 provided on the rear side X2.

  In the heat exchanger 1 of this example, the heat generating element mounting surface 13 (hereinafter, the heat generating element mounting surface 13 of the bottom wall 22 is referred to as a "second heat generating element mounting surface 132") also on the outer surface of the bottom wall 22. Have. On the second heat generating body mounting surface 132, for example, a heat generating body having a smaller amount of heat generation than the heat generating body mounted on the first heat generating body mounting surface 131 can be mounted. Specifically, on the second heating element mounting surface 132, a heating element such as a capacitor can be mounted. These heating elements can be mounted, for example, in a region corresponding to the lower portion Z2 of the fin group 71 (see FIGS. 4 and 8) described later.

  Further, as shown in FIG. 1 and FIG. 2, the front wall 23 and the rear wall are respectively attached to the edge of the front X 1 and the edge of the rear X 2 and the pair of edges in the lateral direction Y of the bottom wall 22. 24 and a pair of side wall parts 25 are erected. The front wall portion 23, the rear wall portion 24, and the pair of side wall portions 25 are joined to the top wall portion 21 at the upper side Z1.

  As shown in FIG. 1 and FIG. 4, the refrigerant supply pipe 14 is attached to the notch portion 221 of the bottom wall portion 22 and extends toward the front X1. Moreover, the refrigerant | coolant discharge pipe 15 is attached to the notch part 222 of the bottom wall part 22, and is extended toward back X2.

  As shown in FIGS. 2 and 5, the main body 2 includes an internal space 200 surrounded by the top wall 21, the bottom wall 22, the front wall 23, the rear wall 24, and the pair of side walls 25. It has the partition plate 3 which divides into a layer. As shown in FIG. 5, the internal space 200 in the main body 2 of this example is a three-layered space 4 (4a, 4b, 4c) aligned in the height direction Z by two partition plates 3 (3a, 3b). Section). In the following, the three-layered space 4 is referred to as the first layer 4a, the second layer 4b and the final layer 4c in order from the top Z1. Moreover, the partition plate 3 which divides the 1st layer 4a and the 2nd layer 4b is called 1st partition plate 3a, and the partition plate 3 which divides the 2nd layer 4b and the last layer 4c is called 2nd partition plate 3b.

  As shown in FIG. 2 and FIG. 5, the heat exchanger 1 of the present example has two first partition plates 3 a arranged in a row at intervals in the lateral direction Y. A gap between the two first partition plates 3a serves as a communication passage 41a (see FIGS. 5 and 6) that causes the first layer 4a and the second layer 4b to communicate with each other.

  Moreover, as shown in FIG.2 and FIG.5, the heat exchanger 1 of this example has the 1st 2nd partition plate 3b which exhibits rectangular shape. As shown in FIGS. 5 and 7, the second partition plate 3 b is disposed apart from the side wall 25 on both sides in the lateral direction Y. A gap between the second partition plate 3b and the side wall 25 is a communication passage 41b for communicating the second layer 4b with the final layer 4c.

  As shown in FIG. 6, the supply header portion 11 for supplying the refrigerant to the first layer 4 a is directed from the both ends of the distribution path portion 111 extended along the front wall portion 23 and both ends of the distribution path portion 111 toward the rear X2. And a pair of extending passage portions 112 which are extended.

  The distribution path portion 111 is provided over the entire lateral direction Y in the main body portion 2, and the distribution wall portion 223 (see FIGS. 6 to 8) erected from the bottom wall portion 22 forms the first layer 4a. , The second layer 4b and the final layer 4c. The distribution passage portion 111 is configured to be able to guide the refrigerant flowing from the refrigerant supply pipe 14 to the pair of extension passage portions 112 while distributing the refrigerant to both sides in the lateral direction Y.

  As shown in FIG. 6, the pair of extension passage portions 112 are provided over the entire longitudinal direction X in the main body portion 2, and can supply the refrigerant into the first layer 4 a from the outside in the lateral direction Y It is configured. In addition, the extension passage portion 112 is such that the flow passage width is gradually narrowed from the proximal end on the distribution passage portion 111 side toward the rear X2.

  As shown in FIGS. 5 and 6, the first layer 4a is a layered space formed between the top wall 21 and the first partition plate 3a. In the first layer 4a, two first heat sinks 5a are arranged side by side with a space in the lateral direction Y. The two first heat sinks 5 a face the extension path portion 112 in the lateral direction Y outward.

  The first heat sink 5a of this example is a laminated heat sink having a refrigerant flow path 62 in which a plurality of plates 6 (see FIG. 9) having a large number of openings 61 are stacked and the openings 61 communicate with each other. is there. As shown in FIG. 9C, the refrigerant flow path 62 of the first heat sink 5a is configured to allow the refrigerant to flow in the lateral direction Y.

  A pair of end surfaces in the longitudinal direction X of the first heat sink 5 a is in contact with the distribution wall 223 and the rear wall 24. The end face of the upper portion Z1 in the height direction Z of the first heat sink 5a is joined to the top wall portion 21, and the end face of the lower portion Z2 is joined to the first partition plate 3a. The end surfaces of the first heat sink 5a in the vertical direction X may be joined to the distribution wall 223 and the rear wall 24. Moreover, the more detailed structure of the 1st heat sink 5a is mentioned later. Moreover, in FIG. 2 and FIGS. 5-8, description of the opening part 61 is abbreviate | omitted for convenience.

  As shown in FIGS. 5 and 7, the second layer 4 b is a layered space formed between the first partition plate 3 a and the second partition plate 3 b. In the second layer 4b, two second heat sinks 5b arranged at intervals in the lateral direction Y are arranged. As shown in FIG. 5, the second heat sink 5b is disposed at a position corresponding to the lower portion Z2 of the first heat sink 5a. In addition, a communication passage 41a communicating the first layer 4a and the second layer 4b is opened between the two second heat sinks 5b.

  The second heat sink 5b in this example is a stacked heat sink having the same configuration as the first heat sink 5a. The second heat sink 5 b has a refrigerant flow path 62 configured to allow the refrigerant to flow in the lateral direction Y. A pair of end surfaces in the longitudinal direction X of the second heat sink 5 b abuts on the distribution wall 223 and the rear wall 24. Further, the end surface of the upper portion Z1 of the second heat sink 5b is joined to the first partition plate 3a, and the end surface of the lower portion Z2 is joined to the second partition plate 3b. The end surfaces of the second heat sink 5 b in the longitudinal direction X may be joined to the distribution wall 223 and the rear wall 24.

  As shown in FIGS. 5 and 8, the final layer 4 c is a layered space formed between the second partition 3 b and the bottom wall 22. A final heat sink 5c is disposed on the final layer 4c.

  As shown in FIG. 8, the final heat sink 5 c of this example is a fin type heat sink having a flat bottom wall 22 and a large number of fins 7 erected from the bottom wall 22. That is, the final heat sink 5 c of this example is integrally formed with the bottom wall portion 22.

  Specifically, the final heat sink 5c in this example has two sets of fin groups 71 spaced apart in the lateral direction Y. Each fin group 71 is disposed at a position corresponding to the lower portion Z2 of the first heat sink 5a and the second heat sink 5b as shown in FIG.

  As shown in FIG. 8, the fin group 71 is composed of a large number of fins 7 arranged in the longitudinal direction X at a constant pitch. The fins 7 in this example are plate fins. As shown in FIG. 5, a gap 42 of about 1 mm exists between the tip of the fin 7 and the second partition plate 3 b.

  As shown in FIG. 8, the discharge header portion 12 is disposed behind the two fin groups 71 at X <b> 2. The discharge header portion 12 communicates with the refrigerant discharge pipe 15 and is configured to be able to lead the refrigerant flowing into the final layer 4 c to the refrigerant discharge pipe 15.

  As described above, the first heat sink 5a and the second heat sink 5b in this example are laminated heat sinks in which a plurality of plates 6 (6a, 6b) having a large number of openings 61 (61a, 61b) are stacked. . As shown in FIGS. 6 and 7, the width dimensions obtained by measuring the first heat sink 5a and the second heat sink 5b in the lateral direction Y are shorter than the length dimensions obtained by measuring them in the longitudinal direction X. .

  The first heat sink 5a and the second heat sink 5b have a four-layer structure in which a first plate 6a shown in FIG. 9A and a second plate 6b shown in FIG. 9B are alternately stacked. .

  As shown in FIG. 9A, the first plate 6a has an opening row 63a consisting of a large number of openings 61a and an opening row 63b consisting of a large number of openings 61b. The opening rows 63a and the opening rows 63b are alternately arranged in the longitudinal direction X at a constant pitch.

  The openings 61 a constituting the opening row 63 a are arranged in the lateral direction Y at a constant pitch. The opening 61a is bent in a V-shape such that the center in the lateral direction Y is positioned behind the both ends X2.

  On the other hand, the openings 61b constituting the opening row 63b are arranged in the lateral direction Y at the same pitch as the openings 61a. Further, the position of the opening 61 b in the lateral direction Y is shifted by a half pitch with respect to the opening 61 a. Each opening 61 b is bent in a V-shape such that the center in the lateral direction Y is positioned on the front X 1 side with respect to both ends.

  The second plate 6b has the same configuration as the first plate 6a except that the position of the opening row 63a and the position of the opening row 63b in the first plate 6a are interchanged as shown in FIG. 9B. doing.

  As an example is shown in FIG.9 (c), the edge part of the opening part 61 in the 2nd plate 6b is an opening part in the 1st plate 6a, when the 1st plate 6a and the 2nd plate 6b are laminated alternately. It is arranged to overlap with the end of 61. As a result, the openings 61 of the adjacent plates 6 communicate with each other, and a refrigerant channel 62 capable of circulating the refrigerant in the lateral direction Y is formed.

  Next, the operation and effect of the heat exchanger 1 will be described. As shown in FIG. 5, the heat exchanger 1 of the present example has a three-layered layered space 4 partitioned by the partition plate 3, and a communication passage in which adjacent layered spaces 4 are provided in the partition plate 3. It communicates by 41. Therefore, the cooling capacity of the heat exchanger 1 can be easily improved.

  The heat exchanger 1 also has a final heat sink 5 c in the final layer 4 c facing the bottom wall 22. And the clearance 42 exists between the front-end | tip of the fin 7 in the final heat sink 5c, and the 2nd partition plate 3b. Thereby, the heat exchanger 1 can easily prevent the rigidity from becoming excessively high.

  Further, the heat exchanger 1 of the present example has the two first heat sinks 5a in the first layer 4a, and the supply header portion 11 guides the refrigerant outward in the lateral direction Y of the two first heat sinks 5a. Is configured as. The first partition plate 3a facing the first layer 4a has a communication passage 41a between the two first heat sinks 5a. Furthermore, the second layer 4b has two second heat sinks 5b, and the second partition plate 3b that divides the second layer 4b and the final layer 4c is downstream of the second heat sink 5b, that is, in the lateral direction. A communication passage 41 b is provided outward in Y.

  In the heat exchanger 1 of the present embodiment, the contact area between the first heat sink 5a and the second heat sink 5b and the refrigerant is obtained by arranging the supply header portion 11, the heat sink 5 and the communication passage 41 so as to have the above specific positional relationship. The flow path length of the refrigerant can be shortened while sufficiently securing the As a result, the heat exchanger 1 of this example can further improve the cooling capacity and can further reduce the pressure loss.

  Further, in the heat exchanger 1 of the present example, a gap 42 exists between the second partition plate 3 b and the final heat sink 5 c. Therefore, when the heat generating body is mounted on the first heat generating body mounting surface 131 and the second heat generating body mounting surface 132, the thermal stress applied to the heat generating body can be reduced. Furthermore, the heat transfer from the first heating element mounting surface 131 to the second heating element mounting surface 132 can be further reduced by the presence of the gap 42. As a result, a larger number of heating elements can be effectively cooled without increasing the volume of the heat exchanger 1.

  Further, as shown in FIG. 6, the heat exchanger 1 of the present example has the extension passage portion 112 formed so that the flow passage width gradually narrows from the distribution passage portion 111 side toward the rear X2. . Thus, the pressure of the refrigerant can be sufficiently increased over the entire length in the longitudinal direction X of the extension path portion 112. As a result, a sufficient amount of refrigerant can be supplied to the entire longitudinal direction X, and thus a sufficient amount of refrigerant can be supplied to the entire first heat sink 5a.

  As a result of the above, the heat exchanger 1 has excellent performance and can improve the life characteristics of the power converter.

  In the first embodiment, an example of the heat exchanger 1 is described in which the supply header 11 guides the refrigerant outward in the direction in which the two first heat sinks 5a are arranged, but the supply header 11 You may be comprised so that a refrigerant | coolant may be guide | induced between two 1st heat sinks 5a. In this case, a communication passage 41a for communicating the first layer 4a and the second layer 4b is disposed outward in the lateral direction Y of the two first heat sinks 5a, and a series for communicating the second layer 4b and the final layer 4c. Preferably, the passage 41b is disposed between the two second heat sinks 5b. Also in the heat exchanger 1 having such a configuration, as in the present example, the effects of the improvement of the cooling performance, the reduction of the pressure loss, and the improvement of the life characteristic can be obtained.

  Although the first heat sink 5a and the second heat sink 5b all have the same configuration in the first embodiment, it is also possible to use heat sinks of different configurations according to the required performance and the like. For example, instead of the laminated heat sink, it is also possible to use a pin fin type heat sink in which a large number of pins are erected from a flat base portion or a corrugated fin type heat sink formed by forming an aluminum plate in a wave shape. Further, although an example in which the opening is bent in a V-shape is shown as an example of the laminated heat sink, the shape of the opening can be appropriately changed as long as the refrigerant can flow in the lateral direction Y.

  Hereinafter, modifications 1 to 3 of the configuration of the first embodiment are specifically shown. Modifications 1 to 3 can exhibit the same effects as those of the first embodiment. Among the reference numerals used in the first to third modifications, the same reference numerals as those used in the first embodiment denote the same constituent elements as those in the first embodiment unless otherwise described.

(Modification 1)
This example is an example of the heat exchanger 1 in which the final heat sink 5d prepared separately from the bottom wall 22 is disposed in the final layer 4c as shown in FIG. The final heat sink 5d of this embodiment is a fin type heat sink having a substantially rectangular base portion 72 and a large number of pin fins 73 erected from the base portion 72, as shown in FIG. As shown in FIG. 11, the base portion 72 of the final heat sink 5d is joined to the second partition plate 3b. A gap 42 is present between the tip of the pin fin 73 and the bottom wall 22. Others are the same as in the first embodiment. The configuration shown in this example can be employed, for example, when the heat generating element is not mounted on the bottom wall portion 22.

(Modification 2)
This example is an example of the heat exchanger 1 in which the final heat sink 5e prepared separately from the bottom wall 22 is disposed in the final layer 4c as shown in FIG. The final heat sink 5e of this example is a corrugated fin formed by processing an aluminum plate into a corrugated shape. The final heat sink 5 e is joined to the second partition plate 3 b at the top 74 of the upper Z 1, and a gap 42 exists between the lower top 75 and the bottom wall 22. Further, the final heat sink 5e of this example is arranged such that the flow path 76 formed between it and the second partition plate 3b extends in the direction parallel to the lateral direction Y. Others are the same as in the first embodiment. The configuration shown in this example can be employed, for example, when the heat generating element is not mounted on the bottom wall portion 22.

(Modification 3)
This example is an example in which the shape of the opening 61 of the plate constituting the laminated heat sink is modified. As shown in FIG. 13, the first plate 6c and the second plate 6d of this example have a large number of rectangular openings 61c, 61d instead of the V-shaped openings 61a, 61b in the first embodiment. ing. The pitch of the openings 61 c and 61 d in the longitudinal direction X and the transverse direction Y is the same as that of the first embodiment.

(Example 2)
This example is an example in which the performance and rigidity of the heat exchanger 102 are evaluated by simulation. In this example, while having the layered space 4 (4a, 4b, 4c) of 3 layers divided by the 1st partition plate 3a and the 2nd partition plate 3b, between the last heat sink 5h and the 2nd partition plate 3b A structural model (model E1, see FIGS. 14 to 20) having a gap 42 was created, and thermal analysis and strain analysis were performed by the finite element method. In addition, for comparison with the model E1, a model C1 having one layered space 4 (FIGS. 21 to 23) and a model C2 having two layered spaces 4 (4a and 4b) (FIGS. 24 to 27) And three layers of layered space 4, and the final heat sink 5h and the second partition plate 3b are in contact with each other to create three structural models of model C3 (FIG. 28), and analysis is performed in the same manner as model E1. The

  The details of each structural model and the analysis procedure will be described below. Among the reference numerals used in FIGS. 14 to 28, the same reference numerals as those used in the first embodiment denote the same constituent elements as those in the first embodiment unless otherwise specified.

[Structure model]
<Model E1>
As shown in FIG. 14, the main body 2 b of the model E 1 has a substantially rectangular parallelepiped shape having a top wall 21 and a bottom wall 22, and the top wall 21 has a heating element mounting surface 13. Further, as shown in FIGS. 15 and 16, the main body portion 2b has two partition plates 3 (3a, 3b) for dividing the inner space 200 into three layered spaces 4 (4a, 4b, 4c). doing. A first heat sink 5f, a second heat sink 5g and a final heat sink 5h are disposed at the centers of the first layer 4a, the second layer 4b and the final layer 4c, respectively.

  As shown in FIG. 14 and FIG. 17, of the four wall portions connecting the top wall portion 21 and the bottom wall portion 22, a pair of wall portions opposed to each other has a refrigerant discharge port 16 at the center in the longitudinal direction. have. The refrigerant discharge port 16 is in communication with either the supply header portion 11 or the discharge header portion 12.

  In this example, the opposing direction of the wall portion having the refrigerant discharge port 16 is referred to as "longitudinal direction X", the supply header portion 11 side in the vertical direction X is "front X1", and the discharge header portion 12 is "rear X2 " The direction in which the top wall 21 and the bottom wall 22 are arranged is referred to as "height direction Z", the side of the top wall 21 in the height direction Z is referred to as "upper Z1", and the side of the bottom wall 22 is " It is called the lower part Z2. In addition, a direction orthogonal to both the longitudinal direction X and the height direction Z is referred to as “horizontal direction Y”. Indications regarding these directions are for convenience.

  As shown in FIGS. 14 and 15, the top wall 21 has a central portion 211 corresponding to the upper portion Z1 of the first heat sink 5f and a peripheral portion 212 surrounding the central portion 211. The central portion 211 is configured to be separable from the peripheral portion 212. When the heat exchanger 102 having the same structure as that of the model E1 is actually manufactured, the central portion 211 is joined to the peripheral portion 212 after the first heat sink 5f is accommodated in the first layer 4a.

  As shown in FIG. 14 and FIG. 15, the peripheral portion 212 and the bottom wall 22 are integrally formed with the front wall 23 and the rear wall 24 having the refrigerant discharge port 16. That is, the main body portion 2b of the model E1 has the box-like body 20 formed of these wall portions and opened on both sides in the lateral direction Y and the upper side Z1. The central portion 211 of the top wall 21 is disposed on the opening surface 201 of the upper portion Z1.

  As shown in FIG.15 and FIG.16, a pair of side wall part 25 (25a, 25b) is arrange | positioned at the opening surface 202 (202a, 202b) of the horizontal direction Y in the box-shaped body 20. As shown in FIG. One of the side wall portions 25 a of the pair of side wall portions 25 is integrally formed with the first partition plate 3 a which is disposed in the upper portion Z 1 of the two partition plates 3. Further, the other side wall portion 25 b is integrally formed with the second partition plate 3 b disposed in the lower portion Z 2 of the two partition plates 3.

  Hereinafter, for convenience, one side wall 25a side in the lateral direction Y is referred to as "right side Y1", and the other side wall 25b side is referred to as "left side Y2". When the heat exchanger 102 having the same structure as that of the model E1 is actually manufactured, one side wall 25a and the first partition plate 3a are inserted into the inside of the box 20 from the opening surface 202a of the right side Y1. The other side wall 25b and the second partition plate 3b are inserted into the inside of the box-like body 20 from the opening surface 202b of the left side Y2.

  As shown in FIGS. 16-18, between the tip of the first partition plate 3a and the other side wall 25b and between the tip of the second partition plate 3b and the one side wall 25a, Each has a gap. A gap between the tip of the first partition plate 3a and the other side wall 25b is a communication passage 41a that allows the first layer 4a and the second layer 4b to communicate with each other. Further, the gap between the end of the second partition plate 3b and the one side wall 25a is a communication passage 41b which allows the second layer 4b and the final layer 4c to communicate with each other.

  As shown in FIG. 17, the supply header portion 11 for supplying the refrigerant to the first layer 4a has a refrigerant flow path provided along the front wall 23 and one side wall 25a. The supply header portion 11 is configured so as to be able to guide the refrigerant flowing from the refrigerant discharge port 16 along the front wall 23 to the right Y1 and then guide it along the one side wall 25a to the rear X2. ing.

  A first heat sink 5 f is disposed at the center of the first layer 4 a. The first heat sink 5f of the model E1 is a laminated heat sink configured to allow the refrigerant to flow in the lateral direction Y.

  A pair of end surfaces in the longitudinal direction X of the first heat sink 5f is in contact with the front wall portion 23, the rear wall portion 24 and a header partition portion 121 (see FIG. 17) described later. The end face of the upper portion Z1 in the height direction Z of the first heat sink 5f is joined to the top wall portion 21, and the end face of the lower portion Z2 is joined to the first partition plate 3a. The end surfaces of the first heat sink 5f in the longitudinal direction X may be joined to the front wall 23, the rear wall 24, and the header partition 121 to be described later. A more detailed configuration of the first heat sink 5 f will be described later. Moreover, in FIGS. 15-18, description of the opening part 61 is abbreviate | omitted for convenience.

  As shown in FIG. 18, a second heat sink 5g having the same configuration as the first heat sink 5f is disposed at the center of the second layer 4b.

  A pair of end surfaces in the longitudinal direction X of the second heat sink 5g abuts on the front wall 23, the rear wall 24, and the header partition 121. Further, the end surface of the upper heat sink Zg of the second heat sink 5g is joined to the first partition plate 3a, and the end surface of the lower heat sink Z2 is joined to the second partition plate 3b. A pair of end faces in the vertical direction X of the second heat sink 5g may be joined to the front wall 23, the rear wall 24, and the header partition 121 to be described later.

  As shown in FIG. 19, the final heat sink 5h is disposed at the center of the final layer 4c. The final heat sink 5 h is a fin type heat sink having a large number of fins 7 erected from the bottom wall 22. Fins 7 of the final heat sink 5h are plate fins and are arranged in the longitudinal direction X at a constant pitch. Further, as shown in FIG. 16, a gap 42 exists between the tip of the fin 7 and the second partition plate 3 b.

  As shown in FIGS. 17-19, the discharge header portion 12 of the model E1 is extended toward the left side Y2 with the refrigerant discharge port 16 of the rear wall portion 24 as a base end. As shown in FIGS. 17 and 18, the discharge header portion 12 is separated from the first layer 4a and the second layer 4b by a header partition portion 121 provided upright on the other side wall portion 25b. In addition, as shown in FIG. 19, the discharge header portion 12 communicates with the final layer 4 c through the through hole 122 provided at the end of the left side Y 2 of the header partition portion 121.

  The first heat sink 5f and the second heat sink 5g are laminated heat sinks having a four-layer structure in which a first plate 6e shown in FIG. 20A and a second plate 6f shown in FIG. 20B are alternately laminated. is there.

  As shown in FIG. 20A, the first plate 6e has a large number of opening rows 63e arranged at a constant pitch in the longitudinal direction X. Each opening row 63e has a large number of openings 61e arranged at a constant pitch in the lateral direction Y. The opening 61 e is bent in a V-shape such that the center in the lateral direction Y is located behind the both ends X 2.

  As shown in FIG. 20B, the second plate 6f has a large number of opening rows 63f arranged in the longitudinal direction X at the same pitch as the opening rows 63e in the first plate 6e. Each opening row 63f has a plurality of openings 61f aligned in the lateral direction Y at the same pitch as the openings 61e in the first plate 6e.

  The opening 61 f is bent in a V-shape such that the center in the lateral direction Y is positioned on the front side X 1 more than both ends. Further, the position of the opening 61 f in the lateral direction Y is shifted by a half pitch with respect to the opening 61 e in the first plate 6 e.

  Although not shown, in the state where the first plate 6e and the second plate 6f are alternately stacked, as in the first embodiment, the end of the opening 61e in the first plate 6e and the second plate 6f And the end of the opening 61f at the end of the opening. As a result, the openings 61 of the adjacent plates 6 communicate with each other, and a refrigerant channel 62 capable of circulating the refrigerant in the lateral direction Y is formed.

The dimensions of each part in the model E1 are as follows.
・ Main part 2b
External dimension in the longitudinal direction X: 75 mm
Outer dimension in the lateral direction Y: 73 mm
External dimension in height direction Z: 14 mm

・ First heat sink 5f and second heat sink 5g
External dimension in the longitudinal direction X: 49 mm
External dimension in the lateral direction Y: 49 mm
External dimension in height direction Z: 4 mm

・ First plate 6e and second plate 6f
Thickness: 1 mm
Pitch P _X in the longitudinal direction X of the opening row 63e and the opening row 63f (see FIG. 20C): 4.9 mm
Pitch P _Y in the lateral direction Y of the opening 61e and the opening 61f: 4.5 mm
Outer dimension L of the opening 61e and the opening 61f in the lateral direction Y: 3.5 mm
Width W of the opening 61: 1 mm
Inclination angle θ of the end of the opening 61 f with respect to the lateral direction Y: 20 degrees

・ Final heat sink 5h
Bottom wall 22 thickness: 1 mm
Fin 7: Width 1 mm x length 49 mm x height 1 mm
Distance between adjacent fins 7: 1.5 mm
Clearance 42: 1 mm between the tip of the fin 7 and the second partition plate 3b

<Model C1>
As shown in FIGS. 21 to 23, the model C1 does not have the partition plate 3 in the internal space 200 of the main body 2c, and a single layered space between the top wall 21 and the bottom wall 22. 4 are formed. Further, one heat sink 5 i is disposed at the center of the layered space 4. The heat sink 5i is a laminated heat sink having an eight-layer structure in which a first plate 6e and a second plate 6f shown in FIG. 20 are alternately stacked. Others are the same as model E1. Among the reference numerals used in FIG. 21 to FIG. 23, the same ones as in FIG. 14 to FIG. 20 indicate the same constituent elements as the model E1 and the like unless otherwise described. Moreover, in FIGS. 21-23, description of the opening part 61 is abbreviate | omitted for convenience.

The dimensions of each part in the model C1 are as follows. The first plate 6 e and the second plate 6 f are omitted because they are the same as the model E 1.
・ Main part 2c
External dimension in the longitudinal direction X: 75 mm
Outer dimension in the lateral direction Y: 73 mm
External dimension in height direction Z: 10 mm

・ Heat sink 5i
External dimension in the longitudinal direction X: 49 mm
External dimension in the lateral direction Y: 49 mm
External dimension in height direction Z: 8 mm

<Model C2>
As shown in FIGS. 24 to 27, the model C2 has one partition plate 3 in the inner space 200 of the main body 2d. As shown in FIG. 25, the internal space 200 of the model C2 is divided by the partition plate 3 into a two-layered space 4 of the first layer 4a and the final layer 4c. The partition plate 3 is integrally formed with the side wall 25a of the right side Y1, as shown in FIG. 24 and FIG. As shown in FIGS. 25 and 26, a gap is present between the tip of the partition plate 3 and the other side wall 25b. The gap serves as a communication passage 41 which causes the first layer 4a and the final layer 4c to communicate with each other.

  As shown in FIGS. 25 to 27, the first heat sink 5j and the final heat sink 5k are disposed at the centers of the first layer 4a and the final layer 4c, respectively. These heat sinks 5 have the same configuration as the first heat sink 5 f in the model E1. That is, the first heat sink 5j and the final heat sink 5k are laminated heat sinks having a four-layer structure in which the first plate 6e and the second plate 6f shown in FIG. 20 are alternately stacked.

  As shown in FIG. 27, the discharge header 12 has a refrigerant flow path provided along one side wall 25 a and the rear wall 24. The discharge header portion 12 is configured such that the refrigerant having passed through the final heat sink 5 k can be guided along the one side wall 25 a to the rear X 2 and then guided along the rear wall 24 to the refrigerant discharge port 16. It is done.

  Others are the same as model E1. Among the reference numerals used in FIG. 24 to FIG. 27, the same ones as in FIG. 14 to FIG. 20 indicate the same components as the model E1 and the like unless otherwise described. Moreover, in FIGS. 24-27, description of the opening part 61 is abbreviate | omitted for convenience.

The dimensions of each part in the model C2 are as follows. The first plate 6 e and the second plate 6 f are omitted because they are the same as the model E 1.
・ Main part 2d
External dimension in the longitudinal direction X: 75 mm
Outer dimension in the lateral direction Y: 73 mm
External dimension in height direction Z: 11 mm

・ First heat sink 5j and final heat sink 5k
External dimension in the longitudinal direction X: 49 mm
External dimension in the lateral direction Y: 49 mm
External dimension in height direction Z: 4 mm

<Model C3>
The model C3 has the same configuration as that of the model E1 except that the tip of the fin 7 in the final heat sink 5c is in contact with the second partition plate 3b as shown in FIG. That is, the model C3 does not have the gap 42 between the final heat sink 5c and the second partition plate 3b. Among the reference numerals used in FIG. 28, the same ones as in FIG. 14 to FIG. 20 indicate the same constituent elements as the model E1 and the like unless otherwise specified. Moreover, in FIG. 28, the description of the opening 61 is omitted for the sake of convenience.

  The dimensions of each part in the model C3 are as follows. The first plate 6e, the second plate 6f, the first heat sink 5a, the second heat sink 5b, and the final heat sink 5c are the same as the model E1 and thus will be omitted.

・ Main part 2e
External dimension in the longitudinal direction X: 75 mm
Outer dimension in the lateral direction Y: 73 mm
External dimension in height direction Z: 13 mm

[Thermal analysis]
The cooling performance and pressure loss of the model E1 and the models C1 to C3 described above were analyzed using analysis software ("SolidWorks® FlowSimulation" manufactured by Dassault Systèmes Solid Works, Inc.). The detailed conditions of thermal analysis are as follows.

-Heating element Two heating elements having a calorific value of 650 W were mounted on the central portion 211 of the top wall 21.
Refrigerant: A 50% aqueous solution of ethylene glycol at 60 ° C. was supplied from the front X 1 of the coolant channel 16 at a flow rate of 5 L / min. Also, assuming that turbulence is generated in the refrigerant on the wall surface of the heat sink, the turbulence parameter is set to 2%.

  The thermal analysis of each model was performed by setting the above conditions, and the maximum temperature of the heating element mounting surface 13 in the steady state and the pressure loss of the refrigerant discharged from the refrigerant guide outlet 16 of the rear X2 were calculated. The results are shown in FIG. The vertical axis in FIG. 29 is the maximum temperature (° C.) of the heating element mounting surface 13 in the steady state, and the horizontal axis is the pressure loss of the refrigerant (kPa), ie, supplied from the refrigerant outlet 16 of the front X1. It is a difference between the pressure (kPa) of the refrigerant and the pressure (kPa) of the refrigerant discharged from the rear side X 2 of the refrigerant introduction port 16.

  As known from FIG. 29, the model E1 had a lower maximum temperature of the heating element mounting surface 13 than the models C1 to C3. In addition, the model E1 has a layered space 4 of three layers, and the pressure loss can be reduced as compared with the model C3 having no gap 42 between the final heat sink 5c and the second partition plate 3b. From these results, it can be understood that the model E1 has excellent cooling performance by having the heat sinks 5 in the three cooling layers respectively, and that the pressure loss can be reduced by the presence of the gap 42.

Distortion analysis
A strain analysis was performed when a load was applied to the model E1 and the models C1 to C3 described above using analysis software (“SolidWorks® Simulation” manufactured by Dassault Systèmes Solid Works, Inc.). Detailed conditions of distortion analysis are as follows.

Restraint Conditions The displacement of both end surfaces 251a and 251b of the main body 2 in the lateral direction Y was restrained, and the other parts were set to be freely displaceable.
-Load condition The load condition which presses the whole surface of the top wall part 21 downward Z2 with uniform pressure was set. The pressure for pressing the top wall 21 was 1 × 10 ⁵ N / m ² .

  The strain analysis of each model was performed by setting the conditions described above, and the maximum value of the displacement of the top wall 21 in the height direction Z in the steady state was calculated. The results are shown in FIG. The vertical axis in FIG. 30 is the maximum value (mm) of the displacement of the top wall 21 in the steady state.

  As known from FIG. 30, the maximum value of the displacement of the top wall 21 in the model E1 is larger than the model C3 and smaller than the models C1 and C2. It can be understood that the rigidity of the model E1 can be reduced by the presence of the gap 42, considering that the external dimension of the model E1 in the height direction Z is the largest among all the structural models. The models C1 and C2 have lower rigidity than the model E1, which may be attributed to the fact that the models C1 and C2 have smaller outer dimensions in the height direction Z than the model E1.

  From the above results, the model E1 has excellent cooling performance and can reduce pressure loss and rigidity.

DESCRIPTION OF SYMBOLS 1 Heat exchanger 11 Supply header part 12 Discharge header part 131, 132 Heating body mounting surface 2, 2b, 2c, 2d, 2e Main body part 21 Top wall part 22 Bottom wall part 3, 3a, 3b Partition plate 4, 4a, 4b , 4c Layered space 41, 41a, 41b Communication passage 5, 5a, 5b, 5c, 5d, 5e, 5f, 5g, 5h, 5i, 5j, 5k Heat sink

Claims (8)

A heat exchanger comprising an aluminum member, wherein
It is formed between a top wall having a heating element mounting surface on which the heating element is mounted on the outer surface, a bottom wall disposed facing the top wall, and the top wall and the bottom wall. A main body having an inner space,
One or more dividers that divide the internal space into layers;
A three- layered space defined by the partition plate and aligned in the opposing direction of the top wall and the bottom wall;
A heat sink disposed in each of the above-mentioned layered spaces, through which a refrigerant flows ;
A communication passage for communicating the adjacent layered spaces;
A supply header portion in communication with the first layer facing the top wall portion among the three- layered space;
And a discharge header portion communicating with the final layer facing the bottom wall portion among the three layers of the layered space,
The first heat sink disposed in the first layer is joined to both the top wall and the first partition plate which is the partition plate facing the first layer,
The final heat sink disposed in the final layer is joined to either the bottom wall portion or the partition plate facing the final layer, and has a gap between the other and the other,
A second layer provided with a second heat sink is provided between the first layer and the final layer,
The second heat sink is disposed between the first heat sink and the final heat sink in the opposing direction of the top wall and the bottom wall, and faces the first partition plate and the final layer. It is joined to both of the second partition plates, which are the partition plates,
The communication passage for communicating the first layer and the second layer is disposed downstream of the first heat sink in the refrigerant flow path,
A heat exchanger characterized in that the communication passage communicating the second layer and the final layer is disposed downstream of the second heat sink in the refrigerant flow path .   The heat exchanger has a second heat generating body mounting surface for mounting the heat generating body on the outer surface of the bottom wall portion, the final heat sink is fixed to the bottom wall portion, and the final heat sink The heat exchanger according to claim 1, wherein a gap is present between the partition plate facing the final layer.   The heat exchanger according to claim 1 or 2, wherein the final heat sink has a flat base portion and a large number of fins erected from the base portion.   The first layer has two of the first heat sinks, and the supply header portion is configured to guide the refrigerant between the two first heat sinks, and is adjacent to the first layer. The heat exchange according to any one of claims 1 to 3, wherein the communication path communicating with the layered space to be fitted is disposed outward in the arranging direction of the two first heat sinks. vessel.   The first layer has two of the first heat sinks, and the supply header portion is configured to guide the refrigerant outward in the direction in which the two first heat sinks are arranged, The heat exchanger according to any one of claims 1 to 3, wherein the communication passage communicating with the adjacent layer is disposed between the two first heat sinks. . Heat exchanger according to claim 5, wherein the second layer is characterized by Tei Rukoto has two of said second heat sink. The first heat sink and the second heat sink are each formed by laminating a plurality of plates having a large number of openings, and having a refrigerant flow path in which the openings of the adjacent plates communicate with each other The heat exchanger according to claim 5 or 6 , characterized in that: In the first heat sink and the second heat sink, the width dimension obtained by measurement in the flow direction of the refrigerant in the state arranged in the layered space is greater than the length dimension obtained by measurement in the direction perpendicular to the flow direction The heat exchanger according to claim 7 , characterized in that it is short.

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