JP4013883B2 - Heat exchanger - Google Patents

Description

  The present invention relates to a heat exchanger. The heat exchanger according to the present invention includes a heat transfer wall or a heat transfer container provided on the heat generating body or a high temperature fluid and a low temperature fluid to dissipate heat generated from an electronic element such as a heat generating element such as a CPU or IGBT. In order to exchange heat with the heat transfer wall, it refers to a heat transfer wall or heat transfer container provided between the fluids.

Conventionally, when transferring heat from a heating element to a fluid to dissipate heat, or when exchanging heat between fluids, heat is exchanged by providing protrusions on the surface of the heat exchanger to increase the heat transfer area and fluid stirring force. The heat transfer from the vessel to the fluid was promoted. For example, there are a heat exchanger with straight fins provided with a plurality of plates on the surface of the heat transfer wall, a heat exchanger with pin fins provided with a plurality of columns on the surface of the heat transfer wall (see, for example, Patent Document 1).
In recent years, the amount of heat generated by electronic elements such as CPUs and IGBTs has increased rapidly, and higher performance heat exchangers are required. Therefore, by reducing the gap between the straight fins or the pin diameter of the pin fins and the distance between the pins, and by integrating the protrusions on the surface of the heat transfer wall, the heat transfer area is increased and the heat transfer of the heat exchanger is increased. Attempts have been made to improve the properties.

JP 2003-47258 A (page 2-3, FIG. 1)

Since the conventional heat exchanger having such a structure is manufactured by microfabrication of protrusions provided on the surface of the heat transfer wall, the cost becomes high, and in some cases, such micromachining may be difficult. There was a problem.
In addition, when the protrusions as described above are provided, the pressure loss accompanying the flow of the cooling fluid increases, so a fan or pump with a higher head is required, which increases the cost and is required. There has been a problem that there may even be no fan or pump with the ability to blow or flow through.
Moreover, since the temperature of the cooling fluid flowing through the heat exchanger rises due to heat reception, the temperature rises as it goes downstream, and as a result, the heat transfer wall temperature on the downstream side rises, resulting in a large temperature distribution in the heat transfer wall surface. There was also a problem.

The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a heat exchanger with low thermal resistance and low pressure loss due to cooling fluid flow at low cost. To do.
Furthermore, it aims at providing the heat exchanger with which the temperature distribution in a heat-transfer wall surface does not produce easily.

Heat exchanger according to this invention, a container cooling fluid inlet and the cooling fluid outlet is provided, the heat transfer as the cooling fluid is distributed along the heat transfer wall of the container which has flowed from the cooling fluid inlet Ribs installed meandering on a surface along the thermal wall, and installed in the container so as to be joined to the ribs, and the interior of the container is connected to the space R1 on the cooling fluid inlet side and the cooling fluid outlet side. A porous body is provided that is divided into a space R2 and allows the dispersed cooling fluid to pass from the space R1 to the space R2.

This invention includes a rib which meanders in the container, in the installed a porous body so as to be joined to the rib, the vessel and the space R1 of the cooling fluid inlet side and a cooling fluid outlet side of the space R2 The cooling fluid passes through a flow passage having a large passage cross-sectional area provided along the heat transfer wall surface and a large number of flow passages in the porous body having a large total surface area. Since the heat exchanger is exchanged, it is possible to provide a heat exchanger with low thermal resistance and low pressure loss due to the flow of the cooling fluid at low cost.

Embodiment 1 FIG.
FIG. 1 is a cross-sectional configuration diagram showing a heat exchanger according to Embodiment 1 of the present invention, FIG. 1 (a) is a cross-sectional configuration diagram along line AA in FIG. 1 (b), and FIG. It is a block diagram. In FIG. 1, the cooling fluid 2 is accommodated in the container 1, and the cooling fluid inlet 4 and the cooling fluid outlet 5 are provided in the container wall. In addition, pipes 6 are provided at the cooling fluid inlets 4, 5, respectively. The heating element 7 that requires heat radiation is provided on the outer wall of the heat transfer wall surface of the container 1. As shown in FIG. 1, a series of meandering porous bodies 3 are accommodated inside the container 1, and the inside of the container is divided into two by the porous body 3.

  The container 1 is a container made of a highly heat conductive material (for example, metal) having an integral structure, or a container composed of an upper lid 8, a side wall 9 and a bottom plate 10. The side wall 9 may be integrated with the top lid 8 or the bottom plate 10. It is preferable to seal the inside of the container by attaching an O-ring or a gasket or filling a filler (for example, an adhesive) to each connection portion of the top lid 8, the side wall 9, and the bottom plate 10.

  As the cooling fluid 2, a gas composed of a single component such as nitrogen or a mixed gas such as air is used. Furthermore, a liquid composed of a single component such as distilled water, ammonia or fluorinate, or a mixed liquid such as an ethylene glycol aqueous solution is used.

  The porous body 3 has voids (pores) such as sintered metal, foam metal, non-woven body (including integrated pin group or plate group), woven body (including laminated wire mesh), and honeycomb formed metal. It is a metal lump or metal group. The porous body 3 is installed in the container so as to divide the inside of the container 1 into a space R1 on the cooling fluid inlet side and a space R2 on the outlet side. Further, the porous body 3 is installed in a meandering manner in the container so that the cooling fluid 2 flowing in from the cooling fluid inlet 4 is dispersed along the heat transfer wall surface of the container 1. The distribution channel 11 and the merging channel 12 have a meandering shape. The meandering shape of the porous body 3 may be a series of meandering shapes as shown in FIG. 1, for example, or may be a series of meandering shapes as shown in FIG. The meandering shape of the porous body 3 is not particularly limited. A series of meandering shapes may be formed by combining a plurality of divided porous bodies 3.

  By installing the porous body 3 having the above configuration in the container, the cooling fluid 2 that has flowed into the space R1 in the container from the cooling fluid inlet 4 passes through the distribution flow path 11 and the heat transfer wall surface of the container 1. (The upper lid 8 in FIG. 1) is distributed along the flow path 13 in the space R1 and adjacent to the porous body 3, passes through the porous body 3, and further flows in the space R2. After passing through the flow path 14 that is a path and adjacent to the porous body 3, it merges in the flow path 12 for merging and flows out from the cooling fluid outlet 5.

  In order to efficiently distribute the cooling fluid 2 and reduce the pressure loss, the flow path 13 is preferably a tapered flow path as shown in FIG.

  In the present embodiment, the porous body 3 is joined to the wall surface of the container 1 on which the heating element 7 is provided by soldering, brazing, pressure welding or the like, but is attached to the container 1 by shrink fitting. Furthermore, in the case of a sintered metal, a foamed metal, etc., it is good to integrally mold with the container 1. Further, for example, a porous body composed of a group of plates and a group of pins may be directly integrally formed on the upper lid or the bottom plate by forging or die casting. FIG. 3 is a perspective view showing an example of the porous body 3 integrally formed on the upper lid 8 by a die casting method. FIG. 3A shows a meander-shaped porous body composed of straight fin groups, and FIG. 3B shows a meander-shaped porous body composed of pin fin groups.

The cooling fluid inlet 4 and the cooling fluid outlet 5 are holes through which the cooling fluid 2 is sent or sent from the pipe 6, and their shapes are not particularly limited.
In addition, the cooling fluid inlet 4 and the cooling fluid outlet 5 may be provided on any same surface of the container 1 or two orthogonal surfaces.

  The pipe 6 is a passage made of a circular pipe, an elliptical pipe, a rectangular pipe, a corrugated pipe (flexible pipe) or the like for transferring the cooling fluid 2, and the material thereof is not particularly limited.

The heat generating element 7 is a heat radiating part of a heat generating element such as an electronic element (for example, CPU, IGBT, etc.), a heat radiating part of a device that transports heat from the heat generating element, or a heat exchanging part when performing heat exchange between fluids A plurality of points may be scattered on the outer wall of the heat transfer wall surface of the container 1 or may be provided on two or more heat transfer wall surfaces of the container 1.
Further, the heating element 7 is provided with a linear expansion coefficient relaxation material or an insulating material (for example, AlN, Al ₂ O ₃ , AlSiC, etc.) provided in the electronic element, or heat to prevent the electronic element from being damaged due to thermal expansion. In addition, a heat radiating portion in which a heat diffusion plate (for example, Cu or the like) provided in order to spread is laminated, and a heat radiating portion in which a plurality of electronic elements are arranged on a substrate (for example, Al, glass epoxy, etc.) are also included.

  Next, the operation of the heat exchanger according to the first embodiment will be described. The cooling fluid 2 is sent from the pipe 6 to the cooling fluid inlet 4, distributed in the distribution channel 11, moves through the channel 13, and has a large number of pores (channels) existing in the porous body 3. , Further moves through the flow path 14, merges in the merging flow path 12, and is sent from the cooling fluid outlet 5 to the pipe 6. At that time, the heat from the heating element 7 is transferred to the porous body 3 by heat conduction through the heat transfer wall surface (for example, the upper lid 8) of the container 1, and is transferred to the cooling fluid 2 passing through the porous body 3. Heat is transferred by heat transfer. Therefore, heat is transferred from the heating element 7 to the cooling fluid 2, the temperature of the cooling fluid 2 rises, and the high-temperature cooling fluid 2 is sent out from the cooling fluid outlet 5, thereby releasing the heat to the outside of the heat exchanger. To do. The heat transferred from the heating element 7 to the cooling fluid 2 via the heat transfer wall surface (for example, the upper lid 8) of the container 1 without passing through the porous body 3 is relatively small.

Since the low-temperature cooling fluid 2 passes through the distribution channel 11 and the channel 13 having a large passage cross-sectional area, the pressure loss is small. Further, since the low-temperature cooling fluid 2 exchanges heat through the flow paths 11 and 13 having a small surface area (heat transfer area, that is, heat exchange amount), the temperature rise of the cooling fluid 2 is small. Moreover, since the said flow paths 11 and 13 spread over the whole heat exchanger, since the said cooling fluid 2 spreads over the whole heat exchanger, the temperature distribution of the whole heat exchanger becomes small.
In addition, the porous body 3 has innumerable pores (flow paths), and since the total heat transfer area in the porous body 3 is large, the heat transfer characteristics are good. Moreover, since the heat transfer characteristic (for example, heat transfer coefficient) from the solid wall to the fluid increases as the flow path diameter (that is, the representative length) decreases, the heat transfer characteristic in the porous body 3 further improves. . In general, the velocity distribution changes significantly at the inlet of the channel, so the heat transfer coefficient is large (leading edge effect). In this embodiment, there are a large number of pores with a short channel length. There are many parts corresponding to, and the heat transfer characteristics are further improved.
On the other hand, the pressure loss accompanying flow increases as the diameter of the pores decreases, but as shown in FIGS. 1 and 2, the channel length of the pores is short, and there are a plurality of parallel channels ( Therefore, the speed of the cooling fluid 2 passing through the flow path is reduced, and the pressure loss is reduced as compared with a heat exchanger having a conventional long flow path.
Further, the high-temperature cooling fluid 2 flowing out through the porous body 3 passes through the flow path 14 and the merge flow path 12 having a large passage cross-sectional area, so that the pressure loss is small.

  In the heat exchanger according to the present embodiment, a large number of small parallel flow paths having a short flow path length exist in a series of meandering porous bodies 3 provided in the container. The low-temperature cooling fluid 2 is uniformly fed from the pipe 6 provided at the fluid inlet 4 through the distribution channel 11. The parallel flow path in the porous body 3 has a large total surface area, and efficiently transfers heat generated in the heating element 7 to the cooling fluid 2 when the cooling fluid 2 passes through the parallel flow path. Further, the high-temperature cooling fluid 2 exchanged in the porous body 3 is sent out from the pipe 6 provided at the cooling fluid outlet 5 through the merging channel 12. As a result, the heat generated in the heating element 7 is dissipated outside the heat exchanger.

  As described above, according to the configuration of the present embodiment, by dividing the inside of the container with a series of meandering porous bodies, a heat exchanger with low thermal resistance and low pressure loss due to the flow of the cooling fluid can be obtained. Can be provided. Further, the cooling fluid distribution / merging channel (distribution channel 11, merging channel 12, channels 13, 14) and the high heat transfer channel (porous body parallel channel) are efficiently along the heat transfer wall surface. By arranging them well, the temperature distribution in the heat transfer wall provided with the heating element 7 is less likely to occur. Further, the use of the porous body 3 that does not require high-cost fine processing can reduce the cost.

Embodiment 2. FIG.
4A and 4B are diagrams showing a heat exchanger according to Embodiment 2 of the present invention, in which FIG. 4A is a disassembled state, FIG. 4B is a longitudinal sectional configuration diagram, and FIG. 4C is a diagram. It is a CC line cross-section block diagram of 4 (b). In the present embodiment, as shown in FIG. 4, ribs 15 having substantially the same shape as the bottom plate-side top shape of the porous body 3 are provided on the inner surface of the container bottom plate 10, and the top lid 8 is interposed via the porous body 3. When the bottom plate 10 is joined, the rib 15 and the porous body 3 are joined. By doing in this way, the passage cross-sectional area of the flow paths 13 and 14 can be made larger than that of the first embodiment. As a result, the pressure loss accompanying the distribution can be further reduced.

In FIG. 4, the cross-sectional shape of the rib 15 is rectangular, but as shown in FIGS. 5B-1 to 5B-3, the shape of the rib 15 on the porous body side is substantially T-shaped, substantially It is better to make it Y-shaped or substantially L-shaped. 5A is a longitudinal sectional configuration diagram, FIGS. 5B-1 to 5B-3 are BB sectional configuration diagrams of FIG. 5A, and FIG. 5C is a diagram. It is a CC line cross-section block diagram of 5 (b-1).
By doing in this way, the flow paths 16, 17 between the ribs communicating with the flow paths 13, 14 between the porous bodies play the same role as the flow paths 13, 14, and the inter-rib flow paths 16, 17 Since the channel cross-sectional area is larger than that of the channels 13 and 14, the width of the channels 13 and 14 can be reduced, and the porous body 3 can be provided more densely in the container. As a result, the heat transfer characteristics of the heat exchanger can be improved.
In addition, when the shape of the rib 15 is substantially Y-shaped or substantially L-shaped, pressing the rib 15 against the porous body 3 deforms the upper end shape of the rib 15 so that the rib 15 and the porous body 3 are in closer contact with each other. In addition, the leakage of the cooling fluid 2 from this portion can be reduced.

  When the shape of the rib 15 on the porous body side is substantially T-shaped, substantially Y-shaped, or substantially L-shaped, the rib 15 is connected to the rib leg portion 15a as shown in FIGS. The heat exchanger may be manufactured by dividing the rib upper end portion 15b and joining the two.

  In the present embodiment, for example, the limit of the volume (particularly the thickness) of the container 1 is not strict, but the fin efficiency of the porous body 3 is deteriorated, so that the height of the porous body 3 cannot be increased. It is particularly effective. Moreover, when the temperature rise of the cooling fluid 2 passing through is large and heat transfer on the downstream side is deteriorated, or when the distance between the cooling fluid inlet 4 and the cooling fluid outlet 5 is long, or the specific heat of the cooling fluid 2 is small. In particular, this is particularly effective in the case of air-cooling heat dissipation or heat exchange in which the temperature rise of the cooling fluid 2 is large and the heat transfer on the downstream side becomes poor.

  In addition, the inflow of the cooling fluid 2 flowing into the porous body 3 directly from the inter-rib flow path 16 or passing through the flow path 13, and the inter-rib flow path 17 directly from the porous body 3 or passing through the flow path 14. In order to improve the outflow of the cooling fluid 2 flowing out to the rib, it is preferable to provide a taper or a curved portion at the rib side end of the porous body 3.

  In the present embodiment, since the bottom plate 10 of the container 1 has a complicated wall shape, the container wall surface (for example, the bottom plate 10) on which the ribs 15 are provided can be manufactured at a lower cost by being integrally formed by resin molding.

In each of the above embodiments, the heating element 7 is provided by inclining or curving the side wall surface (3a in FIG. 5 (b-1)) of the porous body 3 facing the space R1 or the space R2 in the container. By increasing the porous body contact area on the heat transfer wall surface side of the container 1 thus obtained, the fin efficiency of the porous body portion can be increased, and the heat transfer characteristics can be improved. Further, when the inclined or curved portion is provided, fabrication by die casting or forging becomes easy (removal from the mold is facilitated), and a finer porous body can be fabricated, improving heat transfer characteristics. .
Further, at that time, if the porosity and pore diameter of the porous body 3 are changed in the height direction of the porous body 3 (H direction in FIG. 5B-1), the above effect becomes more remarkable. That is, if the side wall surface of the porous body 3 is inclined, the flow path length at the tip side (rib side) is short and the base side (heat transfer wall surface side) is long, so that the cooling fluid can easily pass through the tip side with small pressure loss. Become. Therefore, by making the flow path on the tip side dense and making the root side rough, it is possible to adjust the pressure loss and allow the fluid to flow uniformly in the porous body.

Embodiment 3 FIG.
FIG. 7 is a view showing a porous body 3 provided in a heat exchanger according to Embodiment 3 of the present invention. FIG. 7A is a plan view showing a state before being molded into the porous body 3, and is composed of a flat plate 18 having notches 18 a on both sides. The flat plate 18 is made of, for example, Al, Cu or the like. FIG. 7B is a perspective view of the porous body 3 after being formed, and is configured by forming the flat plate 18 into a corrugated shape.

  The porous body 3 formed in this way can easily form a denser porous body 3, and can realize improvement in heat transfer characteristics and cost reduction.

Embodiment 4 FIG.
FIG. 8 is a cross-sectional configuration diagram showing a heat exchanger according to Embodiment 4 of the present invention. FIG. 8 (a) is a vertical cross-sectional configuration diagram, and FIGS. 8 (b-1) to (b-3) are FIG. FIG. 8C is a cross-sectional configuration diagram along line BB in FIG. 8B-1.
In the present embodiment, the shape of the porous body 3 is not a meandering shape as in the first to third embodiments, but a plurality of shapes are provided in the porous body surface along the heat transfer wall as shown in FIG. It has a ladder shape having a long hole 3b. Moreover, although the rib 15 is provided in the inner surface of the baseplate 10 of the container 1 similarly to Embodiment 2, the rib 15 and the porous body 3 are not the same shape, and the rib 15 has a meandering shape. . That is, the rib 15 provided on the bottom plate 10 is installed meandering in the container so that the cooling fluid 2 flowing in from the cooling fluid inlet 4 is dispersed along the heat transfer wall surface of the container 1, When the upper lid 8 and the bottom plate 10 are joined via the porous body 3, the porous body 3 and the rib 15 are joined, and the interior of the container 1 is a space R1 on the cooling fluid inlet side and a space R2 on the outlet side. It is comprised so that it may be divided. The porous body 3 allows the dispersed cooling fluid 2 to pass from the space R1 to the space R2.
The shape of the rib 15 is substantially T-shaped, substantially Y-shaped, or substantially L-shaped as in FIGS. 5 (b-1) to (b-3), and the porous body 3 is between the rib 15 and the rib 15. Channels 16 and 17 communicating with the channels 13 and 14 therebetween are configured.

  Since the inter-rib flow paths 16 and 17 communicate directly with the distribution flow path 11 and the merge flow path 12, the flow paths 13 and 14 between the porous bodies 3 adjacent to the inter-rib flow paths 16 and 17. May not directly communicate with the distribution flow path 11 and the merge flow path 12, and is a path through which the cooling fluid 2 is passed from the inter-rib flow path 16 through the porous body 3 to the inter-rib flow path 17. You can just play the role of That is, as shown in FIG. 8A, even if the shape of the porous body 3 is not a meandering shape or a ladder shape having a plurality of long holes in the surface of the porous body, it plays the above role. It becomes possible. As a result, notches can be eliminated on both sides of the porous body 3, and it is difficult to break. Also, the manufacture becomes easy.

  In particular, as in the third embodiment, when the porous body 3 is formed by forming a flat plate into a corrugated shape, the manufacture becomes easy. FIG. 9 shows a case where the porous body 3 is molded in this way. FIG. 9A is a plan view showing a state before being molded into the porous body 3, and is composed of a flat plate 19 provided with a plurality of long holes 19 a. The flat plate 19 is made of, for example, Al, Cu or the like. FIG. 9B is a perspective view of the molded porous body 3 and is formed by forming the flat plate 19 into a corrugated shape. The porous body 3 formed in this way can easily form a denser porous body 3, and can realize improvement in heat transfer characteristics and cost reduction. Moreover, since there is no notch at both ends, the notch portion does not open, and installation at the time of manufacture is easy and manufacture becomes easy.

Embodiment 5 FIG.
FIG. 10 is a diagram showing a porous body 3 provided in a heat exchanger according to Embodiment 5 of the present invention. FIG. 10A is a plan view showing a state before the porous body 3 is formed, and is constituted by a grooved flat plate 20 having notches 20a on both sides. FIGS. 10B-1 to 10B-3 are cross-sectional views taken along line B-B in FIG. The grooved flat plate 20 is a flat plate surface with a notch groove as shown in FIG. 10 (b-1), and the flat plate as shown in FIG. 10 (b-2) is deformed into an uneven shape. 10 or a plate meandering in a corrugated shape as shown in FIG. 10 (b-3). In each figure, the direction of the groove is provided in a direction perpendicular to the notch 20a, that is, a direction in which the cooling fluid 2 passes through the corrugated porous body 3 from the space R1 to the space R2. FIG. 10C is a perspective view of the porous body 3 after being formed, and is configured by forming the grooved flat plate 20 into a corrugated shape.
The direction of the groove is not necessarily a direction orthogonal to the notch 20a, but may be inclined from the above direction.

  By doing in this way, the more dense porous body 3 can be shape | molded easily and the improvement of a heat-transfer characteristic and cost reduction can be implement | achieved. Further, the surface area per unit volume can be increased, and the heat transfer characteristics are further improved. In particular, in the grooved flat plate 20, when a corrugated plate and an adjacent plate are in contact with each other, only the groove portion forms a flow path and exhibits higher heat transfer characteristics.

  In the above embodiment, the porous body 3 has a meandering shape, but may have a ladder shape similar to that of the fourth embodiment.

Embodiment 6 FIG.
In each of the above embodiments, the porous body 3 has an example of a meandering shape or a ladder shape along the heat transfer surface. However, as shown in FIG. The porous body 3 may be used. That is, the passage cross-sectional area of the flow paths 13 and 14 may be zero. In FIG. 11, FIG. 11 (a) is an exploded view of the container, FIG. 11 (b) is a longitudinal sectional view, and FIG. 11 (c) is a sectional view taken along line CC in FIG. 11 (b).
In the present embodiment, the cooling fluid 2 is distributed in the distribution channel 11, passes through the inter-rib channel 16, is distributed along the heat transfer wall surface of the container 1, and is a porous body facing the space R <b> 1. 3 directly flows in, passes through the porous body 3, further flows out of the porous body 3 facing the space R <b> 2, passes through the inter-rib channel 17, merges in the merging channel 12, and then exits the cooling fluid outlet 5. Spill from.
By doing in this way, the porous body 3 can be provided in the whole heat-transfer wall surface, a heat-transfer area increases and a heat-transfer characteristic improves.

Embodiment 7 FIG.
FIG. 12 is a cross-sectional configuration diagram showing a heat exchanger according to Embodiment 7 of the present invention. 12 (a) is a longitudinal sectional view, FIG. 12 (b) is a sectional view taken along the line BB in FIG. 12 (a), and FIG. 12 (c) is a sectional view taken along the line CC in FIG. 12 (b). It is.
In the present embodiment, as shown in FIG. 12C, meandering ribs 15 along the heat transfer wall surface of the container 1 are provided on the side wall 9 of the container 1. The rib 15 has a substantially T-shaped, substantially Y-shaped or substantially L-shaped shape at both ends. Further, ladder-shaped porous bodies 3c and 3d are disposed on both sides of the rib 15, respectively, and when the top lid 8, the bottom plate 10 and the side wall 9 are joined, the rib 15 is sandwiched from both sides by the porous bodies 3c and 3d. It is configured as follows. By the bonding, the porous body 3 c is bonded to the upper lid 8 and the rib 15, and the porous body 3 d is bonded to the bottom plate 10 and the rib 15.
In FIG. 12, the rib 15 is provided on the side wall 9 of the container 1. However, the rib 15 is installed in the container separately from the side wall 9 and is configured to be sandwiched from both sides by the porous bodies 3 c and 3 d. It may be.

  By doing in this way, while being able to exchange heat efficiently on both surfaces of the container 1, the flow paths 16 and 17 of the cooling fluid 2 can be shared, and it becomes compact.

  In the above embodiment, the porous bodies 3c and 3d are ladder-shaped, but may have a meandering shape similar to that of the second embodiment.

Further, in the present embodiment, the rib 15 may be a rib 15 with a partition 15c as shown in FIG. In FIG. 13, FIG. 13 (a) is a longitudinal sectional view, FIG. 13 (b) is a sectional view taken along the line BB in FIG. 13 (a), and FIG. 13 (c) is a view taken along line CC in FIG. It is a line section lineblock diagram.
By doing so, the cooling fluid 2 flows out from the distribution channel 11 to the merging channel 12 through two different flow paths formed on both sides of the partition 15c. The flow rate of the cooling fluid 2 to each flow passage can be adjusted by the position of the partition. For example, as shown in FIG. 13, when the partition 15 c is moved to the left side, the cross-sectional area of the left passages 16 and 17 decreases, and the pressure loss associated with the flow increases. On the contrary, in the right flow paths 16 and 17, the passage cross-sectional area becomes large and the pressure loss accompanying the flow becomes small. Therefore, the flow rate varies depending on the pressure loss gap. Therefore, the flow rate toward the heat transfer wall that should have a large heat dissipation capacity is increased, and the flow rate toward the heat transfer wall that may have a small heat dissipation capacity is increased. It can be easily reduced. As a result, heat can be radiated efficiently.

Embodiment 8 FIG.
14 is a view showing a heat exchanger according to an eighth embodiment of the present invention, FIG. 14 (a) is a perspective view, and FIG. 14 (b) is a cross-sectional configuration view taken along line BB in FIG. 14 (a). . In the present embodiment, two heat exchangers are stacked so that the low temperature fluid 2a and the high temperature fluid 2b flow through each of them. Each of the two heat exchangers has the same configuration as the heat exchanger shown in each of the above embodiments, and is stacked so as to share the upper lid 8 of each heat exchanger.
By doing in this way, a higher performance fluid-fluid heat exchanger can be provided.

FIG. 15 is a view showing another heat exchanger according to Embodiment 8 of the present invention, in which the heat exchangers are further laminated in multiple layers.
FIG. 16 is a view showing still another heat exchanger according to Embodiment 8 of the present invention, in which two heat exchangers in which the low temperature fluid 2a and the high temperature fluid 2b flow are formed into a roll shape. is there. By constituting in this way, it can be made more compact.
In addition, a plurality of heat exchangers may be connected in parallel or in series to form a heat exchanger, and a heat exchanger capable of radiating heat or exchanging heat from a distributed heat source can be provided.

It is a section lineblock diagram showing the heat exchanger by Embodiment 1 of the present invention. It is a section lineblock diagram showing other heat exchangers by Embodiment 1 of the present invention. It is a perspective view which shows the example of the porous body which concerns on Embodiment 1 of this invention. It is a figure which shows the heat exchanger by Embodiment 2 of this invention. It is a section lineblock diagram showing other heat exchangers by Embodiment 2 of the present invention. It is a section lineblock diagram showing other heat exchangers by Embodiment 2 of the present invention. It is a figure which shows the porous body provided in the heat exchanger by Embodiment 3 of this invention. It is a section lineblock diagram showing the heat exchanger by Embodiment 4 of the present invention. It is a figure which shows the porous body provided in the other heat exchanger by Embodiment 4 of this invention. It is a figure which shows the porous body provided in the heat exchanger by Embodiment 5 of this invention. It is a block diagram which shows the heat exchanger by Embodiment 6 of this invention. It is a section lineblock diagram showing the heat exchanger by Embodiment 7 of the present invention. It is a cross-sectional block diagram which shows the other heat exchanger by Embodiment 7 of this invention. It is a figure which shows the heat exchanger by Embodiment 8 of this invention. It is a figure which shows the other heat exchanger by Embodiment 8 of this invention. It is a figure which shows the other heat exchanger by Embodiment 8 of this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Container, 2 Cooling fluid, 2a Low temperature fluid, 2b High temperature fluid, 3, 3c, 3d Porous body, 3a Side wall surface of porous body, 3b, 19a Long hole, 4 Cooling fluid inlet, 5 Cooling fluid outlet, 6 Piping 7 Heating element 8 Top lid 9 Side wall 10 Bottom plate 11 Distribution flow path 12 Merge flow path 13 14 Flow path 15 Rib 15a Rib leg 15b Rib upper end 15c Partition 16 17 Inter-rib channel, 18, 19 flat plate, 18a, 20a notch, 20 grooved flat plate.

Claims (14)

Containers and cold却流fluid inlet and a cooling fluid outlet is provided,
Ribs installed meandering on the surface along the heat transfer wall so that the cooling fluid flowing in from the cooling fluid inlet is dispersed along the heat transfer wall of the container;
And the inside of the container is divided into a space R1 on the cooling fluid inlet side and a space R2 on the cooling fluid outlet side, and the dispersed cooling fluid is A heat exchanger comprising a porous body that passes from the space R1 to the space R2. The porous body, heat exchanger according to claim 1, characterized in that the rib substantially the same shape. In each space R1, R2, the cross-sectional area of the flow path between the ribs formed between the ribs is the flow of the flow path formed between the porous body joined to the ribs. The heat exchanger according to claim 1 or 2 , wherein the heat exchanger is larger than a road cross-sectional area. The heat exchanger according to claim 3 , wherein the shape of the rib on the porous body side is substantially T-shaped, substantially Y-shaped, or substantially L-shaped. The heat exchanger according to any one of claims 1 to 4 , wherein the rib is integrally formed with a part of the container by resin molding. The heat exchanger according to any one of claims 1 to 5 , wherein a porous body is disposed on both sides of the rib, and the rib is sandwiched between the porous body. The porous body, heat exchanger according to claim 1, characterized by using a porous body having a plurality of elongated holes in the plane. The heat exchanger according to any one of claims 1 to 6 , wherein the porous body is a corrugated flat plate having a notch. The porous body, heat exchanger according to claim 1, characterized in that is obtained by forming a plate having a plurality of elongated holes in corrugated. The heat exchanger according to claim 8 or 9 , wherein the porous body formed in a corrugated shape is provided with a groove on a flat plate surface in a direction in which the cooling fluid passes through the porous body. The heat exchanger according to any one of claims 1 to 10 , wherein the porous body has an inclined or curved side wall surface facing the space R1 or the space R2 in the container. The heat exchanger according to any one of claims 1 to 11 , wherein the porous body and the container are integrally formed. A heat exchanger according to any one of claims 1 to 12 , wherein heat exchangers according to any one of claims 1 to 12 are stacked, and fluids having different temperatures are allowed to flow through each of the heat exchangers to perform heat exchange between the fluid and the fluid. Exchanger. A heat exchanger according to claim 13 , wherein the heat exchanger is formed into a roll shape.

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