JP2011003708A - Heat exchanger using corrugated heat radiation unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce component cost and bonding operation cost by composing, with a small number of components, a heat exchanger capable of exhibiting an excellent heat radiation effect by controlling the flow of a cooling fluid, in a heat exchanger provided with a heat radiation fin for transferring heat to a cooling fluid on a base plate for thermally connecting a heat generation component thereto.SOLUTION: The heat exchanger is configured such that the corrugated heat radiation unit 10 is used as a heat radiation fin; fluid guide means 17, 18 for guiding the flow of a cooling fluid having flowed in from an entrance part 15 in a plane parallel to a plate surface of a base plate are arranged on the base plate 1; the cooling fluid is guided from the entrance part to the corrugated heat radiation unit; and the flow of the cooling fluid is guided such that the cooling fluid is guided to an exit part 16 after generally uniformly passing through multiple voids (cooling fluid passages) between facing plate surfaces in the corrugated heat radiation unit.

Description

  The present invention relates to a heat exchanger used for heat dissipation of various electronic components such as CPUs, integrated circuits and semiconductor elements, electronic devices, and other various electric devices, and is particularly excellent in heat dissipation efficiency and has a small number of components. It relates to a heat exchanger that is easy to manufacture.

  As is well known, a heat exchanger is often provided for heat dissipation in electronic components such as CPUs, integrated circuits, and semiconductor elements, electronic devices, and various electric devices. A typical example of this type of heat exchanger is shown in FIG.

  In FIG. 21, a base plate 1 to which a heat source such as a CPU, an integrated circuit, or a semiconductor element is thermally connected is made of a metal having high thermal conductivity such as aluminum, copper, or an alloy thereof. On 1, a plurality of long plate-like radiating fins 2 made of a metal having a high thermal conductivity are erected in parallel to constitute a heat exchanger 3 as a whole. As a manufacturing method of such a heat exchanger, since the method of integrally forming the base plate 1 and the heat radiating fins 2 by extrusion is advantageous from the viewpoint of cost, it has been widely applied conventionally, and the base plate and the heat radiating fins are also used. Are separately manufactured, and a method of manufacturing them by joining them is also applied.

  When the conventional general heat exchanger shown in FIG. 21 as described above is actually used, for example, air is used as a cooling fluid, and the base plate 1 is moved from one end as shown by an arrow P in FIG. The air is blown in the direction along the upper surface and along the longitudinal direction (the direction along the plate surface of the plate-like heat radiation fins 2), and air is allowed to flow between the adjacent heat radiation fins 2, thereby causing the heat generating component to pass through the base plate 1 The heat transmitted to the plate-like heat radiation fins 2 is radiated into the atmosphere.

  By the way, in such a conventional general heat exchanger, the length of the plate-shaped radiating fin (the length in the direction from the windward side to the leeward side of the cooling air) is long, or adjacent plate-shaped radiating fins If the distance between the two is small, cold air is in contact with the surface of the leeward portion of the radiating fin, but the air that is in contact with the leeward portion of the radiating fin has already risen in temperature. In addition to not being able to obtain a sufficient heat dissipation effect as a whole, there is a problem that heat dissipation of heat-generating components that are thermally connected in the vicinity of the leeward side of the radiating fin in the base plate is not sufficiently performed. .

  Here, it is conceivable to increase the spacing between the radiating fins and to flow a large amount of cooling air at a high speed in order to improve the cooling efficiency. Only air can pass through the central part at high speed, and heat exchange is not performed sufficiently.

  As described above, the conventional heat exchanger shown in FIG. 21 does not provide a sufficient heat dissipation effect. In particular, when cooling a plurality of heat generating components arranged vertically, the heat generating component on the leeward side is particularly effective. It was not possible to cool down.

  In order to solve such a problem, a heat exchanger as shown in Patent Document 1 has already been proposed. The heat exchanger shown in Patent Document 1 basically reduces the flow velocity of cooling air flowing between a large number of plate-like heat dissipating fins, so that the temperature boundary layer (ie, the cooling air flow is The part of the air flow that rises in temperature by passing through the surface of the radiating fin and passing the heat when passing between the parts, and the part of the air flow that is away from the surface of the radiating fin that is not affected by the heat of the radiating fin So that the surface temperature of the plate-like heat radiation fins of the heat exchanger is on average close to the temperature of the leeward side (heat exchanger outlet side). It was made based on the idea that

  Some examples of the structure of the heat exchanger of the invention of Patent Document 1 are shown in FIGS. Of these, a typical example of FIG. 19 will be described. In this example, at least one heat generating component is thermally connected to the base plate 1, and the base plate 1 has a predetermined length along the longitudinal direction thereof. At least one plate-shaped heat radiation fin 2 (five plate-shaped heat radiation fins 2 arranged in the vertical direction in the example of FIG. 19) arranged in parallel at an angle and thermally connected to the base plate 1. In the example shown in FIG. 19, three fin portions 4 are arranged in the horizontal direction and these constitute a fin group as a whole, and cooling air is supplied to each of the at least one fin portion 4. The flow of the cooling air is guided so that the cooling air is decelerated between the plate-like heat radiation fins 2 in each of the inlet portion 5 to be fed and each of the at least one fin portion 4 so as to flow almost uniformly. That the baffle plate 6 and the partition plate portion 7, is provided an outlet 8 for discharging the cooling air, the heat exchanger 3 is configured as a whole.

  According to the invention proposed in Patent Document 1 as described above, the cooling capacity is high with the same envelope volume, and there is almost no temperature difference in the windward and leeward direction (that is, cold air contacts the fins even in the leeward). An excellent heat exchanger can be obtained. In particular, in the case of a heat exchanger having a long base plate on which heat dissipating fins are disposed, a heat exchanger having a remarkably excellent heat dissipating efficiency can be obtained.

JP 2008-205421 A

  The heat exchanger proposed in Patent Document 1, for example, the heat exchanger shown in FIG. 19, has a larger number of plate-like radiating fins 2 than the conventional heat exchanger shown in FIG. Therefore, it is difficult to manufacture the radiating fins 2 integrally with the base plate 1. Therefore, it is necessary to manufacture the plate-shaped heat radiation fins 2 and the base plate 1 separately. In this case, however, there is a problem that the number of heat radiation fins to be manufactured increases, and the manufacturing cost of the parts is significantly increased. Further, in order to thermally and closely join the plate-shaped heat radiation fins 2 to the base plate 1, even when a method such as brazing or soldering is used, it is necessary to arrange a large number of heat radiation fins 2 on the base plate 1. For this reason, if the number of fins is large, the work of arranging the fins takes time and there is a problem that the work cost increases.

  The present invention has been made against the background described above, and has excellent heat exchange efficiency equivalent to the heat exchanger proposed in Patent Document 1, and is sufficient even on the leeward side of the cooling fluid. An object of the present invention is to provide a heat exchanger that can easily manufacture a heat exchanger capable of exhibiting a heat dissipation effect with a significantly smaller number of parts than the heat exchanger proposed in Patent Document 1. .

As a result of repeated investigations on the means for solving the above problems by the present inventors, instead of the plate-like heat dissipating fins arranged in parallel in Patent Document 1, they are replaced by a corrugated heat dissipating unit. It has been found that the above problem can be solved, and the present invention has been made.

  Here, the corrugated heat radiating unit is one end side in the longitudinal direction of the plate as a cross-sectional shape obtained by cutting an elongated strip-like plate by a plane perpendicular to the plate surface and parallel to the length direction of the plate. Means a corrugated shape (wave shape) in which peaks and troughs are alternately reversed and bent toward the other end side, and a space where the plate surfaces face each other is used as a cooling fluid passage. Such a heat radiating unit is arranged so that the cooling passage is substantially parallel to the base plate with respect to the base plate, that is, the direction from one opening end of the cooling passage toward the other opening end is relative to the surface of the base plate. In order to function as a heat radiating member, it is erected on the base plate so as to be substantially parallel to each other.

  The specific configuration of the corrugated heat radiating unit as described above will be described later in detail, but typically, as shown in FIG. There is one in which the S-shape is made continuous by being inverted and bent so that the U-shape is alternately directed in the opposite direction from one side to the other side in the vertical direction.

  Also, as shown in FIG. 4, the elongated strip-shaped plate is turned into a cross-sectional shape, and inverted and bent so that the U-shape is alternately directed in the opposite direction from one end side to the other end side in the length direction of the plate. Some have a continuous shape.

  Further, as shown in FIG. 5, an elongated strip-like plate is reversed and bent so that the cross-sectional shape is V-shaped alternately from one end side to the other end side in the length direction of the plate. There is a continuous W-shape.

  Furthermore, there are other combinations of two or more U-shape, U-shape, and V-shape as described above, for example, as shown in FIG.

  In such a corrugated heat radiating unit, the space between the mutually facing plate surfaces of the strip-shaped plate that is the material of the corrugated plate can be made to function as a heat radiating member by forming a cooling fluid passage. It is.

  Specifically, the present invention is as follows.

  That is, the heat exchanger provided with the corrugated heat dissipating unit of the invention of claim 1 is provided with a heat dissipating unit for transferring heat to a cooling fluid on a base plate to which heat generating components are thermally connected. In the heat exchanger, the heat exchanger has an inlet portion into which the cooling fluid flows in and an outlet portion from which the cooling fluid flows out, and the heat radiating unit has an elongated belt-like plate orthogonal to the plate surface and As a cross-sectional shape cut by a plane parallel to the length direction, the plate surface as a corrugated shape in which peaks and troughs are alternately reversed and bent alternately from one end side to the other end side in the length direction of the plate Is used as a cooling fluid passage, and the heat dissipating unit is erected on the base plate so that the cooling passage is substantially parallel to the base unit. On the rate, fluid guiding means for guiding the flow of the cooling fluid flowing in from the inlet portion in a plane parallel to the plate surface of the base plate is provided, and the fluid guiding means is a cooling fluid. From the inlet portion to one opening end of each cooling fluid passage between the plate surfaces of the heat dissipation unit, and the cooling fluid passes through each cooling fluid passage in the heat dissipation unit from the other opening end. The cooling fluid is guided so as to be led to the outlet portion.

  The invention according to claim 2 is the heat exchanger provided with the corrugated heat dissipation unit according to claim 1, wherein the cross-sectional shape of the heat dissipation unit is directed from one end side to the other end side in the length direction of the plate. The S-shape is made continuous by being inverted and bent so that the U-shape is alternately directed in the opposite direction.

  Further, the invention of claim 3 is the heat exchanger provided with the corrugated heat dissipation unit according to claim 1, wherein the cross-sectional shape of the heat dissipation unit is directed from one end side to the other end side in the length direction of the plate. The U-shape is inverted and bent so as to be alternately directed in the opposite direction, and the self-shape is made continuous.

  The invention of claim 4 is the heat exchanger provided with the corrugated heat dissipating unit according to claim 1, wherein the cross-sectional shape of the heat dissipating unit is changed from one end side to the other end side in the length direction of the plate. The V-shape is reversed and bent so as to alternately face in the opposite direction, and the shape is made continuous with the W-shape.

  Furthermore, the invention of claim 5 is the heat exchanger according to any one of claims 1 to 4, wherein the fluid guiding means sends the cooling fluid from the inlet portion to each of the heat dissipation units. The cooling fluid passage is made to flow substantially along the surface where the one open ends of the cooling fluid passages are arranged, and further, the cooling fluid passages of the heat radiating unit are made to pass substantially uniformly, and the other of the cooling fluid passages of the heat radiating unit is The flow of the cooling fluid is guided so as to flow toward the outlet portion substantially along the surface on the side where the open ends are arranged.

  The invention according to claim 6 is the heat exchanger according to any one of claims 1 to 5, wherein the fluid guiding means is one open end of each cooling fluid passage in the heat dissipation unit. In the space on the side where the cooling plates are arranged, except for the inlet and the cooling fluid passages of the heat radiating unit, the cooling fluid flows out in the plane parallel to the plate surface of the base plate and the fluid other than the cooling fluid flows in. In the space on the side where the other opening end of each cooling fluid passage in the heat radiating unit is lined up with the first partition wall for preventing the cooling, except for each cooling fluid passage and the outlet portion of the heat radiating unit, The second partition for preventing the cooling fluid from flowing out and the fluid other than the cooling fluid from flowing in a plane parallel to the plate surface.

  Still further, the invention according to claim 7 is the heat exchanger according to claim 6, wherein the first partition wall is substantially perpendicular to a surface separated from the heat radiating unit and aligned with one open end of each cooling fluid passage. A first side wall plate provided so as to be, and a heat radiation unit end on the outlet side and the first side wall plate in a space where one opening end of each cooling fluid passage of the heat radiation unit is arranged. A first baffle plate connected to each other, and the second partition wall is provided so as to be substantially parallel to a surface on the side where the other opening ends of the cooling fluid passages are arranged apart from the heat radiating unit. 2 side wall plates, and a second baffle plate for connecting the heat radiation unit end portion on the inlet side and the second side wall plate in the space on the side where the other opening end is arranged. It is a feature.

  The invention according to claim 8 is the heat exchanger according to claim 6, wherein the first partition is provided in a space on the side where one open end of each cooling fluid passage of the heat radiating unit is arranged. 3, and in the space on the one opening end side, the distance between the heat radiating unit and the third side wall plate gradually decreases from the inlet side toward the outlet side. The second partition is provided in a space on the side where the other open ends of the cooling fluid passages of the heat dissipation unit are arranged, so that the two are substantially in contact with each other at the end of the heat dissipation unit on the side. In the space on the other opening end side of the heat radiating unit, the space between the heat radiating unit and the fourth side wall plate gradually decreases from the outlet side toward the inlet side. The heat dissipation unit end on the inlet side In is characterized in that both are configured to abut substantially.

  Furthermore, the invention of claim 9 is the heat exchanger according to any one of claims 1 to 5, wherein two of the heat dissipating units are provided, and the fluid guiding means is The two heat dissipating units are arranged so that the distance between the two heat dissipating units gradually decreases from the inlet side toward the outlet side, and these two heat dissipating units are mutually connected at the end of the heat dissipating unit on the outlet side. It is comprised by arrange | positioning so that it may contact | connect.

  The invention of claim 10 is the heat exchanger according to any one of claims 6 to 9, wherein the combination of the heat dissipation unit, the partition wall, the side wall plate, and the baffle plate described in these claims. The arrangement consisting of is repeated a plurality of times in the horizontal direction or the vertical direction in a plane parallel to the plate surface of the base plate.

  The invention according to claim 11 is the heat exchanger according to claim 2, wherein the heat radiating unit is compressed and deformed from both sides of the entire surface continuously reversed in an S shape and cooled between the plate surfaces. The fluid passage is narrowed.

According to the present invention in which a corrugated heat radiating unit is used, a heat exchanger that can exhibit an excellent heat radiating effect by controlling the flow of the cooling fluid can be configured with a small number of parts, and therefore, component manufacturing The cost can be reduced, and the joining work for thermal connection between the heat radiating unit and the base plate can be simplified, and the working cost can be reduced.
In addition, since the number of parts is small as described above, there is a low possibility that the heat radiating unit falls off the base plate, and high reliability can be obtained.

  Further, the corrugated heat radiating unit itself can be manufactured by using a strip-like elongated plate as a raw material and easily processed using a press or a corrugator. However, when these processing methods are used, high dimensional accuracy is obtained. be able to.

  Further, when a so-called brazing sheet in which a brazing material is clad with a core material is used as the material plate of the corrugated heat dissipation unit, the number of parts can be further reduced.

  Moreover, the corrosion resistance of the corrugated heat dissipation unit can be improved by using a clad material made of a combination of a sacrificial anticorrosive material and a core material as the material plate of the corrugated heat dissipation unit.

  Furthermore, as defined in claim 2, a corrugated heat dissipation unit is used in which an elongated belt-like plate is inverted and bent so that the U-shape is alternately directed in the opposite direction, and the S-shape is continuous. In this case, as defined in claim 11 and as shown in FIG. 7, each gap of the corrugation (i.e., cooling) is pressed and compressed from both sides (i.e., in the directions of arrows A and B). The passage of the working fluid) can be narrowed, so that the heat transfer efficiency can be increased and the heat exchange efficiency can be further increased. In this case, in practice, after processing the plate into a corrugated shape, the corrugated shape may be placed in a square cylindrical casing and pressed from the A and B directions with a press or the like. The cooling fluid passage can be realized very easily, and the heat exchange efficiency can be further enhanced.

FIG. 1 is a schematic partially cutaway perspective view showing a heat exchanger according to a first embodiment of the present invention. FIG. 2 is a schematic plan view of the heat exchanger according to the first embodiment of the present invention shown in FIG. FIG. 3 is a schematic diagram showing a cross-sectional shape of a corrugated heat dissipation unit formed by bending a U-shape of a cross-section U continuously into an S-shape and bending it so as to repeat peaks and valleys. FIG. 4 is a schematic diagram showing a cross-sectional shape of a corrugated heat radiating unit having a U-shaped cross-sectional shape that is inverted and continuously bent into a self-shaped shape. FIG. 5 is a schematic diagram showing a cross-sectional shape of a corrugated heat dissipation unit formed by bending a cross-sectional V-shape into a W-shape and continuously bending it so as to repeat ridges and valleys. FIG. 6 is a schematic view showing a cross-sectional shape of a corrugated heat dissipation unit that is bent so that a U-shaped cross-section and a U-shaped cross-section are alternately positioned, and is formed so as to repeat a peak and a valley in a wavy shape. FIG. 7 is a schematic diagram showing a state where the corrugated heat radiating unit is pressed and compressed from both ends of the corrugated to narrow the cooling fluid passage. FIG. 8 is a schematic perspective view showing a heat exchanger according to a second embodiment of the present invention. FIG. 9 is a schematic plan view of the heat exchanger according to the second embodiment of the present invention shown in FIG. FIG. 10 is a schematic perspective view showing a heat exchanger according to a third embodiment of the present invention. FIG. 11 is a schematic plan view of the heat exchanger according to the third embodiment of the present invention shown in FIG. FIG. 12 is a schematic partially cutaway perspective view showing a heat exchanger according to a fourth embodiment of the present invention. FIG. 13 is a schematic perspective view showing a heat exchanger according to a fifth embodiment of the present invention. FIG. 14 is a schematic perspective view showing a heat exchanger according to a sixth embodiment of the present invention. FIG. 15 is a schematic partially cutaway perspective view showing a first structural example of a conventionally proposed heat exchanger. FIG. 16 is a schematic plan view of the heat exchanger shown in FIG. FIG. 17 is a schematic plan view showing a second structural example of a conventionally proposed heat exchanger. FIG. 18 is a schematic plan view showing a third structural example of a conventionally proposed heat exchanger. FIG. 19 is a schematic perspective view showing a fourth structural example of a conventionally proposed heat exchanger. FIG. 20 is a schematic perspective view showing a fifth structural example of a conventionally proposed heat exchanger. FIG. 21 is a schematic perspective view showing a typical example of a conventional general heat exchanger.

  Embodiments of the present invention will be described below with reference to the drawings.

  1 and 2 show a heat exchanger according to a first embodiment corresponding to the inventions of claims 1, 2, 5, and 6. In FIG. 1, a part of the heat exchanger (a part of a first side wall plate 19 described later) is cut out.

  In the heat exchanger of the embodiment shown in FIGS. 1 and 2, the corrugated heat radiating unit 10 whose cross-sectional shape is shown in FIG. 3, that is, a heat radiating unit corresponding to claim 2 is used. That is, the heat radiating unit 10 basically has an elongated strip-shaped metal plate 11 as a cross-sectional shape cut by a plane orthogonal to the plate surface and parallel to the plate length direction. A corrugated shape (wave shape) in which peaks and troughs are alternately reversed from one end side to the other end side, and a space where the plate surfaces face each other is defined as a cooling fluid passage 13. Then, in particular, as the cross-sectional shape, from the one end side to the other end side in the length direction of the plate, the U-shape is alternately inverted and bent so as to face in the opposite direction, and the S-shape is made continuous. Something is used.

  The strip-shaped metal plate 11 constituting the corrugated heat dissipation unit 10 may be a single plate (bare material) made of a metal having good thermal conductivity such as aluminum, copper, or an alloy thereof. A brazing sheet may be used in which a brazing material is clad on one or both sides with a simple metal plate as a core material, and further, a sacrificial anode material clad on one side of the metal plate as described above, or a single-sided brazing material A brazing sheet with a sacrificial anode material clad on one side may be used.

  In FIG. 1 and FIG. 2, a base plate 1 is one in which heat generating components such as a semiconductor element, an integrated circuit, and a CPU (not shown) are thermally connected to the back side, and heat conduction such as aluminum, copper, or an alloy thereof. The corrugated heat radiating unit 10 is erected on the front side of the base plate 1, for example, in the form of a rectangular thick plate made of a material having good properties. In other words, the cooling fluid passages 13 are substantially parallel to the surface of the base unit 1, that is, in the example shown in the drawing, the plates of the portions parallel to each other of the strip-shaped metal plates 11 constituting the corrugated heat dissipation unit 10. The surface is erected on the base plate 1 so that the surface is substantially perpendicular to the surface of the base unit 1. And the inversion bending part (cross-sectional U-shaped part) in such a corrugated heat radiating unit 10 is being fixed in the state thermally connected to the plate surface of the base plate 1. Further, the portion on the near side of the space above the base plate 1 is an inlet portion 15 into which cooling fluid flows, and the inner portion is an outlet portion 16 from which cooling fluid flows out.

  Further, on the base plate 1, the flow of the cooling air is parallel to the plate surface of the base plate 1 between the inlet portion 15 into which the cooling fluid, for example, air flows, and the outlet portion 16 from which the cooling air flows out. A first partition wall 17 and a second partition wall 18 are provided as fluid guiding means for guiding in the plane.

  The first partition wall 17 is formed in the space on the side where one open end of each cooling fluid passage 13 in the corrugated heat radiating unit 10 is lined (hereinafter referred to as “one open surface 10A side”). Except for the fluid passages 13 of the portion 15 and the corrugated heat dissipation unit 10 for preventing the outflow of cooling air and the inflow of fluids other than the cooling fluid in a plane parallel to the plate surface of the base plate 1; In other words, with the exception of the inlet portion 15 and each fluid passage 13, it is for partitioning from adjacent portions in a plane parallel to the plate surface of the base plate 1. The second partition wall 18 has a corrugated shape in a space on the side where the other opening ends of the cooling fluid passages 13 are lined up in the corrugated heat dissipation unit 10 (hereinafter referred to as “the other opening surface 10B side”). Except for the fluid passages 13 and the outlet portion 16 of the heat radiating unit 10, for preventing the outflow of cooling air and the inflow of fluids other than the cooling fluid in a plane parallel to the plate surface of the base plate 1, In other words, with the exception of the outlet portion 16 and each fluid passage 13, it is for partitioning from adjacent portions in a plane parallel to the plate surface of the base plate 1. Here, as can be understood from the above, the opening surfaces 10A and 10B in the corrugated heat radiating unit 10 are positioned so that both ends in the width direction of the band-shaped metal plate 11 which is the base plate of the corrugated heat radiating unit 10 are aligned. It means each side of the side.

  The first partition wall 17 includes a first side wall plate 19 provided so as to be separated from the corrugated heat dissipation unit 10 and substantially parallel to the one opening surface 10A, and one opening surface 10A of the corrugated heat dissipation unit 10. The first baffle plate 21 that connects the corrugated heat radiation unit end portion on the outlet portion 16 side and the first side wall plate 19 on the side of the outlet portion 16 is formed. The second partition wall 18 includes a second side wall plate 20 provided so as to be separated from the corrugated heat dissipation unit 10 and substantially parallel to one opening surface 10B, and the other opening surface of the corrugated heat dissipation unit 10. On the 10B side, the corrugated heat radiation unit end on the inlet 15 side and the second baffle plate 22 connecting the second side wall plate 20 are configured.

  Here, the materials of the side wall plates 19 and 20 and the baffle plates 21 and 22 constituting the first partition wall 17 and the second partition wall 18 are not particularly limited, and workability or bondability is taken into consideration. Of course, an appropriate material may be used, and of course, an alloy having good thermal conductivity such as aluminum, copper, or an alloy thereof similar to the base plate 1 or the corrugated heat dissipation unit 10 may be used.

  In the example shown in FIGS. 1 and 2, the first and second baffle plates 21 and 22 are provided so as to be substantially horizontal with respect to the opening surfaces 10 </ b> A and 10 </ b> B of the corrugated heat dissipation unit 10. Of course, the baffle plates 21 and 22 may be provided at an angle with respect to the opening surfaces 10A and 10B. Further, the first side wall plate 19 and the first baffle plate 21 do not need to be made as separate members. In some cases, the first side wall plate 19 and the first baffle plate 21 may be made as a single plate, or the second side wall plate. Similarly, the second baffle plate 20 and the second baffle plate 22 may be made of a single plate as an integral unit.

  Here, means for fixing the corrugated heat radiation unit 10 in a state of being thermally connected to the base plate 1 is not particularly limited, but may be coupled by, for example, brazing, soldering, bonding, mechanical caulking, or the like. Furthermore, these may be used in combination. Among these, it is most preferable to apply brazing from the viewpoint of thermal bonding. When joining by brazing, brazing material may be arranged near the joint as a separate member from the corrugated heat dissipation unit, but brazing is clad on one or both sides of the core material as a metal plate of the corrugated heat dissipation unit material If a so-called brazing sheet is used, the number of parts can be reduced. Of course, when the corrugated heat radiating unit 10 is fixed on the base plate 1 by press-fitting or mechanical caulking, heat conduction grease or the like may be used together.

  Moreover, the corrugated heat dissipation unit 10 can be easily manufactured by processing a band-shaped metal plate of a raw material using a press or a corrugator, and according to these processing methods, high dimensional accuracy can be obtained.

  Moreover, the corrosion resistance of the corrugated heat radiating unit can be improved by making the material of the corrugated heat radiating unit 10 a clad material made of a combination with the sacrificial anticorrosive material as described above.

  Further, in the case of a corrugated heat dissipation unit produced by bending the shape of the cross-section U into an S-shape as a long and narrow strip-like metal plate 11 and bending it so as to repeat a peak and a valley in a wavy shape, FIG. As shown in FIG. 2, the gaps (that is, the cooling fluid passages 13) of the corrugation can be narrowed by pressing and compressing them from both sides, that is, in the directions of the arrows A and B. In this case, actually, after processing into a corrugated shape, it may be placed in a rectangular cylindrical casing and pressed from the A and B directions with a press or the like. In this way, a narrow cooling fluid passage can be realized very easily.

  1 and FIG. 2 as described above, the situation at the time of use in the heat exchanger of the first embodiment, particularly the air flow (air flow) when air is used as the cooling fluid and the heat dissipation situation by the air flow Will be described next.

  For example, a high-speed air flow sent by a fan (not shown) or the like is sent from the inlet portion 15 into a substantially rectangular parallelepiped space between the one opening surface 10A of the corrugated heat dissipation unit 10 and the first side wall plate 19. . In this space, the high-speed air flow flows to the back of FIG. 2 along the opening surface 10A and the plate surface of the first side wall plate 19, and the flow is blocked by the first baffle plate 21 in the innermost portion. The direction is turned, enters each cooling fluid passage 13 of the corrugated heat dissipation unit 10 from the opening surface 10A side, is sent to the opening surface 10B side, and is a space between the opening surface 10B and the second side wall plate 20 And are discharged from the outlet portion 16 to the outside. In this process, after the air flow flows in from the inlet portion 15 as described above, the direction of the air flow is turned by the first baffle plate 19 in the back so as to be dispersed and flowed into the multiple fluid passages 13. The speed is reduced and the fluid passages 13 pass almost uniformly as a low-speed air flow. Then, while the low-speed air flow passes through each fluid passage 13, heat is taken from the surfaces of the metal plates 11 on both sides of each fluid passage 13, and the temperature rises and is sent to the outlet portion 16 from the opening surface 10 </ b> B side. become. As described above, the air flow sent at a high speed passes through the numerous fluid passages 13 in the corrugated heat dissipation unit 10 almost uniformly as a low-speed air flow, so that excellent heat dissipation performance can be obtained. .

  Here, among the structural examples of the heat exchanger shown in Patent Document 1 already described, structural examples corresponding to the first embodiment of the present invention are shown in FIGS. 15 and 16, and FIG. The conventional heat exchanger shown in FIG. 16 is compared with the heat exchanger according to the first embodiment of the present invention shown in FIGS. In Patent Document 1, “plate fins”, “fin portions”, and “fin groups” are defined as follows. That is, each plate-like fin 2 is erected on the plate surface of the base plate 1 in FIGS. 15 and 16, and the fin portion 4 is a plate-like fin 2 as shown in FIGS. 15 and 16. The whole thing arranged in a line in the vertical direction. In addition, the fin group is formed by arranging the plurality of fin portions 4 as a whole, that is, for example, as shown in FIG.

  In the heat exchanger described in Patent Document 1 as shown in FIGS. 15 and 16, the fin portion 4 is configured by arranging a large number of plate-like fins 2 in parallel on the base plate 1 at a predetermined angle. Thus, the cooling air passes between the adjacent plate-like fins 2. In such a structure, the number of the plate-like fins 2 to be handled becomes extremely large, the manufacturing cost of parts increases, and at the same time, a large cost is required for the operation of arranging the plate-like fins 2 on the base plate 1.

  On the other hand, in the heat exchanger of the present invention, particularly the heat exchanger of the embodiment shown in FIGS. 1 and 2, the plate-like fins referred to in Patent Document 1, that is, the heat exchanger shown in FIGS. The plate-like fins 2 are replaced with corrugated heat dissipation units 10. For this reason, the number of members to be handled (members corresponding to plate-like fins in Patent Document 1) is significantly smaller than that of the heat exchanger of Patent Document 1, and therefore the heat exchanger is configured with a small number of parts. As a result, it has become possible to significantly reduce the cost of manufacturing parts and the cost of joining operations.

  8 and 9 show a heat exchanger according to a second embodiment corresponding to each of the inventions of claims 1, 5 and 7. 8 and 9, the same elements as those shown in FIGS. 1 and 2 are denoted by the same reference numerals, and detailed description thereof is omitted.

  8 and 9, a corrugated heat radiation unit 10 similar to the above is erected on the base plate 1, and the first partition wall 17 as the fluid guiding means is formed by the third side wall plate 23 and the second wall plate 23. The partition wall 18 is constituted by a fourth side wall plate 24. That is, the third side wall plate 23 is erected on the side of one opening surface 10A of the corrugated radiating unit, and the fourth side wall plate 24 is erected on the other opening surface 10B side of the corrugated radiating unit 10. In addition, the third side wall plate 23 has a gap between the plate surface and one opening surface 10A of the corrugated heat dissipation unit 10 gradually becoming narrower from the inlet portion 15 toward the outlet portion 16, so that corrugated heat dissipation is achieved. The fourth side wall plate 24 is arranged so that both are in contact with each other at the end portion on the outlet portion 16 side of the unit 10, and the distance between the plate surface and the other opening surface 10B of the corrugated heat dissipation unit 10 is the outlet portion. 16 is gradually narrowed from the side of 16 toward the side of the inlet portion 15, and is arranged so that both are in contact with each other at the end portion on the side of the inlet portion 15 in the inlet portion corrugated heat radiation unit 10.

  In the second embodiment shown in FIGS. 8 and 9, one side wall plate 19 provided substantially parallel to one opening surface 10A of the corrugated heat dissipation unit 10 in the first embodiment is used. In addition, instead of the single baffle plate 21 provided substantially perpendicular to the opening surface 10A, a single side wall plate 23 is provided obliquely with respect to the opening surface 10A, and in the first embodiment, a corrugated shape. Instead of one side wall plate 20 provided substantially parallel to the other opening surface 10B of the heat radiation unit 10 and one baffle plate 22 provided substantially perpendicular to the opening surface 10A, one sheet By providing the side wall plate 24 obliquely with respect to the opening surface 10B, it can be said that the same function as in the case of the first embodiment is achieved.

  In addition, in addition, in FIGS. 8 and 9, the opening surfaces 10 </ b> A and 10 </ b> B of the corrugated heat radiating unit 10 are arranged so as to be parallel to the direction from the inlet portion 15 to the outlet portion 16. Although the plates 23 and 24 are depicted as being arranged at an angle, the side wall plates 23 and 24 are actually arranged in parallel to the direction from the inlet 15 to the outlet 16. The opening surfaces 10A and 10B of the corrugated heat dissipation unit 10 may be arranged at an angle. Alternatively, both the opening surfaces 10A and 10B and the side wall plates 23 and 24 of the corrugated heat dissipation unit 10 may be arranged so as to form an angle with respect to the direction from the inlet portion 15 toward the outlet portion 16. Of course.

  In this embodiment, the materials for the third and fourth side wall plates 23 and 24 are the same as those described for the first and second side wall plates 19 and 20 in the first embodiment. As a method of fixing the third and fourth side wall plates 23, 24 to the plate surface of the base plate 1, a method similar to the method described above can be applied.

  The flow of cooling air (air flow) when actually using the heat exchanger of the second embodiment shown in FIGS. 8 and 9 is basically shown in FIGS. Although it is almost the same as the case of the first embodiment, it will be briefly described here again.

  A high-speed air flow sent from the outside of the heat exchanger to the inlet portion 15 flows into the space between the third side wall plate 23 and the one opening surface 10A of the corrugated heat dissipation unit 10 from the inlet portion 15. It is sent to the back. Here, on one opening surface 10A side of the corrugated heat radiating unit 10, the distance between the opening surface 10A and the plate surface of the third side wall plate 23 gradually decreases from the inlet portion 15 side toward the back. Since the corrugated radiating unit 10 and the third side wall plate 23 are arranged in contact with each other at the fin end on the innermost outlet portion 16 side, the high-speed air flow turns around the inlet portion. 15 in a direction returning to 15 and being dispersed in a large number of gaps (fluid passages 13) in the corrugated heat dissipation unit 10 during that time, almost uniformly in a state where the speed is reduced (a state where a low-speed air flow is formed). The fluid flows in each fluid passage 13, passes through each fluid passage 13, and exits to the other opening surface 10 </ b> B side of the corrugated heat dissipation unit 10. On the opening surface 10B side, the opening surface 10B and the fourth side wall plate 24 are in contact with each other at the fin end on the inlet portion 15 side, and the distance between the opening surface 10B and the fourth side wall plate 24 is the inlet portion 15. Therefore, the air flow that has passed through each fluid passage 13 of the corrugated heat dissipation unit 10 is guided to the outlet portion 16 and flows out of the heat exchanger from the outlet portion 16. .

  Here, among the structural examples of the heat exchanger shown in Patent Document 1, FIG. 17 shows a structural example corresponding to the second embodiment of the present invention. The heat exchanger of FIG. The second embodiment of FIG. 8 and FIG. 9 is compared.

  In the heat exchanger described in Patent Document 1 shown in FIG. 17, the fin portion 4 is configured by arranging a large number of plate-like fins 2 in parallel at a predetermined angle on the base plate 1. In such a structure, the number of plate-like fins 2 to be handled is extremely large, the manufacturing cost is increased, and a large cost is required for the work of arranging a large number of plate-like fins 2 on the base plate 1.

  On the other hand, in the heat exchanger of the second embodiment of the present invention, the plate-like fin 2 referred to in Patent Document 1 is replaced with a corrugated heat dissipation unit 10 as in the case of the first embodiment described above. The fin part 4 as referred to in Patent Document 1 is an integral part of the corrugated heat dissipation unit 10. For this reason, the number of members to be handled (members corresponding to plate-like fins in Patent Document 1) is significantly smaller than that in Patent Document 1, and the heat exchanger can be configured with a small number of parts. Therefore, it is possible to significantly reduce the parts manufacturing cost and the joining work cost.

  10 and 11 show a heat exchanger according to a third embodiment of the present invention corresponding to claims 1, 2 and 6.

  In the heat exchanger of the third embodiment shown in FIGS. 10 and 11, two corrugated heat radiation units 10-1 and 10-2 are erected on the base plate 1. These two corrugated heat radiation units 10-1 and 10-2 have an interval (interval between opening surfaces) that gradually decreases from the inlet portion 15 toward the outlet portion 16. The unit ends are positioned so as to contact each other.

  The fluid flow path of the corrugated heat radiating unit used here is inclined with respect to the opening surface of the corrugation, and is arranged so that the pressure loss is low and the cooling air flows easily.

  Here, in the heat exchanger of the third embodiment shown in FIGS. 10 and 11, the first partition wall 17 (specifically, in the first embodiment) in the first and second embodiments described above. Corresponds to the first side wall plate 19 and the first baffle plate 21, and corresponds to the third side wall plate 23 in the second embodiment, and the second partition wall 18 (specifically, the first embodiment). In the example, it corresponds to the second side wall plate 20 and the second baffle plate 22, and in the second embodiment, it corresponds to the fourth side wall plate 24). This is because the arrangement form of the two corrugated heat radiation units 10-1 and 10-2 itself is a fluid guiding means.

  Therefore, the flow of cooling air (cooling air) in the heat exchanger of the third embodiment will be described.

  A high-speed air flow is sent to the heat exchanger from the outside to the inlet portion 15 opened between the front end portions of the two corrugated heat radiation units 10-1 and 10-2. The airflow flows into a space between one opening surface 10A of each of the two corrugated heat dissipation units 10-1 and 10-2. Here, the distance between the two corrugated heat radiation units 10-1 and 10-2 gradually decreases from the inlet 15 side toward the back, and at the end of the unit on the innermost outlet 16 side. Since they are arranged so that they are in contact with each other, the high-speed air flow described above turns in the left and right directions, and into a large number of gaps (fluid passages 13) in the two corrugated heat dissipation units 10-1 and 10-2. Head. As in the case of the first and second embodiments described above, the speed is reduced by being dispersed in a large number of gaps, and the air flows into the numerous gaps (fluid passages 13) almost uniformly as a low-speed air flow. In the meantime, heat is taken from the metal plate in the corrugated heat radiating unit 10 during that time, and the air flow exiting each fluid passage 13 flows into the corrugated heat radiating units 10-1, 10-2. From the other opening surface 10B to the outlet 16. As described above, in the case of the third embodiment shown in FIGS. 10 and 11, the two corrugated heat radiation units 10-1 and 10 are provided although no partition wall made of a side wall plate or a baffle plate is provided. -2 arrangement mode itself leads the air flow from the inlet portion 15 to the corrugated heat dissipation units 10-1 and 10-2, and the multiple fluid passages 13 ( The gaps between the corrugated heat dissipating units) can be substantially uniformly passed and guided to the outlet portion 16.

  In the examples shown in FIGS. 10 and 11, the unit end portions are positioned so as to be in direct contact with each other on the outlet portion 16 side, but the unit end portions on the outlet portion 16 side are required. Need only be substantially in contact with each other. For example, they may be in indirect contact with each other via a partition-like small part (not shown), and voids (cooling fluid passages) in a number of corrugated heat dissipation units. As long as the gap is small enough not to affect the airflow flowing through 13), the end portions of the units may be close to each other and a small gap may exist between them.

  Here, among the structural examples of the heat exchanger shown in Patent Document 1, FIG. 18 shows a structural example corresponding to the third embodiment of the present invention, and the heat exchanger of FIG. A comparison is made with the heat exchanger of the third embodiment of the present invention shown in FIG.

  In the heat exchanger described in Patent Document 1 shown in FIG. 18, a single fin portion 4 is configured by arranging a large number of plate-like fins 2 in parallel at a predetermined angle on the base plate 1. A fin group is configured by arranging the fin portions 4 in a square shape when seen in a plan view.

  In such a configuration, the number of the plate-like fins 2 to be handled becomes extremely large and the manufacturing cost increases, and a large cost is required for the work of arranging a large number of plate-like fins 2 on the base plate 1.

  On the other hand, in the heat exchanger according to the third embodiment of the present invention, the two fin portions 4 each including a plurality of plate-like fins 2 referred to in Patent Document 1 are respectively corrugated heat radiation units 10-1, 10-2 is an integral part. For this reason, the number of members to be handled (members corresponding to plate-like fins in Patent Document 1) is significantly smaller than that in Patent Document 1, and the heat exchanger can be configured with a small number of parts. Therefore, it is possible to significantly reduce the parts manufacturing cost and the joining work cost.

  On the other hand, in the heat exchanger of the present invention, the arrangement structure in each embodiment shown in FIGS. 1, 2, and 8 to 11 is arranged in the lateral direction (the direction orthogonal to the direction from the inlet portion 15 toward the outlet portion 16. ) Or in the vertical direction (the direction from the inlet portion 15 toward the outlet portion 16) may be repeated a plurality of times, examples of which are shown in FIGS. 12 to 14 and Patent Document 1 corresponding to these examples. An example of the structure shown in FIG. 19 is shown in FIGS.

  That is, FIG. 12 shows a fourth embodiment of the present invention in which the arrangement structure in the first embodiment shown in FIGS. 1 and 2 is repeated plural times in the horizontal direction, and the conventional proposal corresponding thereto is shown. An example of the structure of this heat exchanger is shown in FIG.

  FIG. 13 shows a fifth embodiment of the present invention in which the arrangement structure in the second embodiment shown in FIGS. 8 and 9 is repeated a plurality of times in the horizontal direction.

  Further, FIG. 14 shows a sixth embodiment of the present invention in which the arrangement structure in the third embodiment shown in FIGS. 10 and 11 is repeated a plurality of times in the horizontal direction, and the conventional proposal corresponding thereto is shown. An example of the structure of the heat exchanger is shown in FIG.

  Here, in each example shown in FIGS. 1, 2, and 7 to 14, the corrugated heat dissipation unit is shown as having the cross-sectional shape shown in FIG. 3. You may use what has the cross-sectional shape in any one of FIG.4, FIG.5, FIG.6.

  That is, FIG. 4 shows the corrugated heat radiating unit 10 whose cross-sectional shape is inverted from one end side to the other end side in the length direction of the elongated strip-shaped metal plate 11 so that the U-shape is alternately directed in the opposite direction. FIG. 5 shows a corrugated heat radiating unit 10 that is bent and has a continuous self-letter shape. One end side in the length direction of a strip-shaped metal plate 11 is shown in FIG. From the other end to the other end side, the V-shape is inverted and bent so as to alternately face in the opposite direction, and the W-shape is continuously formed. You may apply to each Example.

  Further, FIG. 6 shows a corrugated heat radiating unit 10 in which a cross-sectional shape of an elongated strip-shaped metal plate 11 is inverted and bent so that U-shaped and U-shaped are alternately positioned, that is, U A combination of a U-shape and a U-shape is shown, and a corrugated heat dissipation unit having such a shape can also be applied to each of the embodiments. In addition, it is of course possible to use a combination of two or more of a U shape, a U shape, and a V shape as appropriate.

  The detailed shape, dimensions, manufacturing method, and the like of the corrugated heat dissipation unit used in the heat exchanger of the present invention are not particularly limited, and may be the same as those in the related art.

  The specific dimensions in the embodiment according to the present invention are such that the cooling fluid passage width of the corrugated radiating unit 10 is 0.5 mm and the length is 2.5 mm, but these numerical values are merely an example. However, it is needless to say that the scope of the present invention is not limited.

  When using such a heat exchanger for heat dissipation of electronic components such as semiconductor elements and electrical components, for example, as in the case of heat dissipation fins of conventional heat exchangers such as comb heat sinks, corrugated heat dissipation Needless to say, a cooling fluid such as air or LLC (Long Life Coolant) needs to be surely passed through the unit. For this purpose, the cooling fluid drive source such as a fan or pump for forcing a cooling fluid such as air to the corrugated heat dissipation unit is used as a cooling fluid, except in the case of natural air cooling where air is flowed by gravity. It is usually located upstream or downstream of the flow.

  In order to ensure that the cooling fluid flows through the portion of the heat exchanger having the corrugated heat radiating unit, it is preferable that the path through which the cooling fluid flows outside the heat exchanger is partitioned by a duct or the like. . When the fan or pump is arranged upstream of the cooling fluid flow, the cooling fluid is not leaked out of the path, and the fan or pump is arranged downstream of the cooling fluid flow. In such a case, it is preferable that the fluid other than the cooling fluid is not mixed from outside the path. The place where these ducts and the like are arranged may be only on the upstream side of the heat exchanger, only on the downstream side, or on both the upstream and downstream sides.

  Similarly, it is preferable that a duct or the like is disposed so as to surround the heat exchanger having the corrugated heat dissipation unit in the portion of the heat exchanger having the corrugated heat dissipation unit. In that case, at least the open part above the corrugated heat dissipation unit must be covered, and as its specific structure, a structure in which the cover is joined and integrated with the upper end of the corrugated heat dissipation unit may be used. Absent. Further, the cover may be a separate part or a single part from a duct or the like disposed only on the upstream side, only on the downstream side, or on both the upstream and downstream sides of the heat exchanger.

  In general, it is not necessary to ensure that the cooling fluid flows in the portion of the heat radiating fin (corrugated heat radiating unit in the case of the present invention). This also applies to conventional heat exchangers.

DESCRIPTION OF SYMBOLS 1 Base plate 10 Corrugated heat dissipation unit 10-1 Corrugated heat dissipation unit 10-2 Corrugated heat dissipation unit 10A, 10B Open surface of corrugated heat dissipation unit 11 Metal plate 13 Cooling fluid passage (gap)
DESCRIPTION OF SYMBOLS 15 Entrance part 16 Outlet part 17 1st partition 18 2nd partition 19 1st side wall plate 20 2nd side wall plate 21 1st baffle plate 22 2nd baffle plate 23 3rd side wall plate 24 4th Side wall plate

Claims (11)

In a heat exchanger in which a heat dissipating unit for conducting heat transfer to a cooling fluid is provided on a base plate to which heat generating components are thermally connected,
The cooling unit has an inlet portion through which a cooling fluid flows in and an outlet portion through which the cooling fluid flows out, and the heat radiating unit has an elongated belt-like plate orthogonal to the plate surface and parallel to the plate length direction. As a cross-sectional shape cut by a flat surface, a corrugated shape in which crests and troughs are alternately reversed from one end side to the other end side in the length direction of the plate, and the gap facing the plate surface is cooled. The fluid passage is used, and the heat dissipation unit is configured to stand on the base plate so that the cooling passage is substantially parallel to the base unit.
Furthermore, fluid guiding means for guiding the flow of the cooling fluid flowing from the inlet portion in a plane parallel to the plate surface of the base plate is provided on the base plate, and the fluid guiding means is a cooling mechanism. The cooling fluid is led from the inlet portion to one opening end of each cooling fluid passage between the plate surfaces of the heat radiating unit, and the cooling fluid passes through each cooling fluid passage in the heat radiating unit and opens to the other side. A heat exchanger provided with a corrugated heat dissipation unit, wherein the flow of cooling fluid is guided so as to be led from the end to the outlet portion. In the heat exchanger provided with the corrugated heat dissipation unit according to claim 1,
The cross-sectional shape of the heat radiating unit is a shape in which the S-shape is continuous by being inverted and bent so that the U-shape is alternately directed in the opposite direction from one end side to the other end side in the length direction of the plate. A heat exchanger provided with a corrugated heat dissipation unit. In the heat exchanger provided with the corrugated heat dissipation unit according to claim 1,
The cross-sectional shape of the heat dissipating unit is a shape in which a self-letter shape is continued by reversing and bending so that the U-shape is alternately directed in the opposite direction from one end side to the other end side in the length direction of the plate. A heat exchanger provided with a corrugated heat dissipation unit. In the heat exchanger provided with the corrugated heat dissipation unit according to claim 1,
The cross-sectional shape of the heat radiating unit is a shape in which a V-shape is inverted and bent alternately in the opposite direction from one end side to the other end side in the length direction of the plate and is continuously formed in a W-shape. A heat exchanger provided with a corrugated heat dissipation unit. In the heat exchanger according to any one of claims 1 to 4,
The fluid guiding means causes the cooling fluid to flow from the inlet portion substantially along a surface along which one open ends of the cooling fluid passages in the heat radiating unit are arranged, and further each cooling fluid passage of the heat radiating unit is substantially provided. The flow of the cooling fluid is guided so as to flow toward the outlet portion substantially along the surface on the side where the other opening ends of the cooling fluid passages in the heat radiating unit are lined up uniformly. A heat exchanger provided with a corrugated heat dissipation unit. In the heat exchanger according to any one of claims 1 to 5,
In the space on the side where one open end of each cooling fluid passage in the heat radiating unit is lined up, the fluid guiding means, except for the inlet fluid passage and each cooling fluid passage in the heat radiating unit, In a space on the side where the first partition wall for preventing the outflow of the cooling fluid in the parallel plane and the inflow of the fluid other than the cooling fluid and the other opening end of each cooling fluid passage in the heat dissipation unit are arranged Except for the cooling fluid passages and the outlet portion of the heat radiating unit, a second for preventing the cooling fluid from flowing out and the fluid other than the cooling fluid from flowing in the plane parallel to the plate surface of the base plate. A heat exchanger provided with a corrugated heat radiation unit.   7. The heat exchanger according to claim 6, wherein the first partition wall is provided so that the first partition wall is separated from the heat radiating unit and is substantially perpendicular to a surface on which one opening end of each cooling fluid passage is arranged. And a first baffle plate that connects the end portion of the heat radiating unit on the outlet side and the first side wall plate in a space where one open end of each cooling fluid passage of the heat radiating unit is arranged. A second side wall plate provided so that the second partition wall is separated from the heat radiating unit and is substantially parallel to a surface on which the other opening ends of the cooling fluid passages are arranged; and the other opening. A corrugated heat dissipating unit comprising a heat dissipating unit end on the inlet portion side and a second baffle plate connecting the second side wall plate in a space where the ends are arranged is provided. Heat exchanger.   The heat exchanger according to claim 6, wherein the first partition is configured by a third side wall plate provided in a space on the side where one open end of each cooling fluid passage of the heat radiating unit is arranged, In the space on the one opening end side, the distance between the heat dissipation unit and the third side wall plate is gradually narrowed from the inlet portion side toward the outlet portion side. The second partition is constituted by a fourth side wall plate provided in a space on the side where the other opening ends of the cooling fluid passages of the heat radiating unit are arranged, and is configured to substantially radiate heat. In the space on the other opening end side of the unit, the space between the heat dissipation unit and the fourth side wall plate gradually becomes narrower from the outlet portion side toward the inlet portion side, so that the heat radiating unit end portion on the inlet portion side Both are in substantial contact Characterized in that it is configured urchin, a heat exchanger having a corrugated heat radiation unit.   The heat exchanger according to any one of claims 1 to 5, wherein two heat dissipating units are provided, and the fluid guiding means is a distance between the two heat dissipating units. Are arranged so as to gradually narrow from the inlet side toward the outlet side, and these two heat radiating units are arranged so as to be in contact with each other at the heat radiating unit end on the outlet side. A heat exchanger provided with a corrugated heat dissipation unit.   The heat exchanger according to any one of claims 6 to 9, wherein an arrangement comprising a combination of the heat dissipation unit, the partition wall, the side wall plate, and the baffle plate described in these claims is a plate of the base plate. A heat exchanger provided with a corrugated heat radiating unit, which is repeated a plurality of times in a horizontal direction or a vertical direction in a plane parallel to the plane.   3. The heat exchanger according to claim 2, wherein the heat radiating unit is configured to have a cooling fluid passage between the plate surfaces narrowed by compressing and deforming from the entire double-sided side that is alternately reversed and continuous in an S-shape. A heat exchanger provided with a corrugated heat dissipation unit.

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