JP4175340B2 - Heat exchanger - Google Patents

Description

  The present invention relates to a heat exchanger that performs heat exchange between a low-temperature fluid and a high-temperature fluid.

Some vehicles such as automobiles are equipped with a thermoelectric generator that generates electric power using exhaust heat of an engine (see, for example, Patent Document 1). In this technique, a plurality of thermoelectric generators arranged above and below the exhaust pipe are sandwiched between a plurality of low temperature side members (heat exchangers) provided corresponding to the respective thermoelectric generators and the exhaust pipe to generate heat. It constitutes a power generator. Each of the low temperature side members is formed in a comb shape, and a plurality of low temperature medium passages are formed in parallel along the medium in / out direction, and the thermoelectric generator is formed by heat exchange with the cooling water supplied from the cooling pipe. Is supposed to cool.
JP 2002-325470 A JP 2002-250572 A JP 2001-44521 A JP-A-5-203289

  However, in the conventional technology as described above, since each cooling pipe on the cooling water inlet / outlet side is connected to the center portion in the width direction of the low temperature side member, the flow of the cooling water flows in the center portion in the width direction inside the low temperature side member. There was a problem that the amount of heat exchanged was reduced.

  In view of the above facts, an object of the present invention is to obtain a heat exchanger in which a fluid as a heat exchange medium flows uniformly in a shell.

In order to achieve the above object, a heat exchanger according to claim 1 is a heat exchanger for exchanging heat between a fluid passing through the shell and a substance contacting the outer surface of the heat transfer wall of the shell. A fluid inlet provided at a central portion in the width direction on one end side of the shell; a fluid outlet provided in a central portion in the width direction on the other end side of the shell; A plurality of fins arranged in parallel with each other in the shell such that each one end is located on one end side of the shell and the other end is located on the other end side of the shell; Diffusing means for diffusing the flow of fluid in the width direction of the shell, provided at one or both between the fluid inlet and one end of the fin and between the other end of the fin and the fluid outlet; wherein the diffusion means, The end of the shell in the width direction is a diffusing member positioned outside the end of the fluid inlet or the outlet of the fluid in the width direction, and the diffusing member has a height along the standing direction of the fins. Is smaller than the height of the fin .

  In the heat exchanger according to claim 1, the fluid introduced into the shell from the fluid inlet performs heat exchange with the fins and the heat transfer wall while passing between the plurality of fins, and passes through the fluid outlet to the outside of the shell. To be derived. Thereby, heat exchange between the fluid passing through the shell and the substance (solid, fluid, etc.) in contact with the outer surface of the heat transfer wall of the shell is performed. Here, since the diffusion means is provided between the fluid inlet and the fin in the shell or between the fin and the fluid outlet, the fluid that tries to pass through the center in the width direction of the shell diffuses in the shell width direction by the diffusion means. (Distributed) and flows uniformly between the plurality of heat collecting members. Thereby, heat exchange efficiency improves.

  Thus, in the heat exchanger according to the first aspect, the fluid as the heat exchange medium flows uniformly in the shell. In addition, it is preferable to close between the wall part facing the heat-transfer wall in a shell, and the edge part of each fin so that the bypass of a fluid becomes substantially impossible.

Further, in this heat exchanger, the end of the diffusion member in the shell width direction is located on the outer side in the width direction than the end of the fluid inlet or the fluid outlet, in other words, at least at the center in the width direction in the shell. Since the dimension connecting the both ends in the width direction of the diffusing member (a plurality of diffusing members) is larger than the dimension along the shell width direction of the fluid inlet or the fluid outlet, the fluid is more effectively transferred to the outer region in the width direction in the shell. Diffused.

Furthermore, in this heat exchanger, the diffusion member whose height is smaller than the height of the fins (the bypass flow path formed therebetween) can pass the fluid in the center in the width direction while diffusing the fluid outward in the width direction. it can.

Heat exchanger according to the second aspect of the present invention, in the heat exchanger of the heat exchanger according to claim 1 Symbol placement, before Symbol diffusion member is formed in a tapered shape projecting into the fluid inlet side .

In the heat exchanger according to claim 2, since the diffusion member arranged on the fluid inlet side or the fluid outlet side with respect to the plurality of heat transfer plates has a tapered shape that protrudes toward the fluid inlet side (upstream side in the flow direction), An increase in flow resistance due to the installation of the diffusion member can be suppressed.

In order to achieve the above object, a heat exchanger according to a third aspect of the present invention is a heat exchanger for performing heat exchange between a fluid passing through a shell and a substance contacting the outer surface of a heat transfer wall of the shell. A fluid inlet provided at a central portion in the width direction on one end side of the shell; a fluid outlet provided in a central portion in the width direction on the other end side of the shell; A plurality of fins disposed parallel to each other in the shell such that one end is located on one side wall side of the shell and the other end is located on the other side wall side of the shell. And a first closing portion that closes between one end of the one fin and the one side wall, and the other end of the fin and the other side wall that are located closer to the fluid outlet than the one fin A second closing portion that closes the space between There.

In the heat exchanger according to claim 3 , the fluid introduced into the shell from the fluid inlet is between the heat collecting members (the first closing portion and the second closing portion) from the other end side to the one end side of the plurality of fins. Heat exchange with the fins and the heat transfer wall while flowing between the heat collecting members positioned between the heat collecting member and the heat collecting member, and is led out of the shell through the fluid outlet. Heat exchange with the substance (solid, fluid, etc.) that contacts the outer surface of the heat transfer wall is performed, where each inlet of the bypass channel between the fins is connected to the other side wall (the other end in the width direction of the shell). And the outlet of the bypass channel between the fins is arranged on one side wall side (one end side in the width direction of the shell), in other words, the flow direction changes when passing between the fins. Because of the structure, the fluid introduced from the center in the width direction of the shell It flows toward the widthwise end after being guided in. Therefore, flowing between the plurality of heat collecting member uniformly fluid. This improves the heat exchange efficiency.

Thus, in the heat exchanger according to the third aspect , the fluid as the heat exchange medium flows uniformly in the shell. In addition, it is preferable to close between the wall part facing the heat-transfer wall in a shell, and the edge part of each fin so that the bypass of a fluid becomes substantially impossible.

A heat exchanger according to a fourth aspect of the present invention is the heat exchanger according to the third aspect , wherein each fin has a distance between one end and the one side wall with respect to the fin adjacent to the fluid inlet side. They are wide and offset from each other so that the distance between the other end and the other side wall is reduced.

5. The heat exchanger according to claim 4 , wherein the distance from one end of each heat transfer plate to one side wall is closer to the outlet side from the fluid inlet side on one wall side, and the fluid inlet side is on the other wall side. The distance from the other end of each heat transfer plate and the other side wall increases from the distance toward the outlet side. For this reason, in this heat exchanger, the fluid easily flows in between the heat transfer plates on the side close to the fluid inlet, but hardly flows out. On the contrary, the fluid hardly flows in between the heat transfer plates on the side close to the fluid outlet. It is easy to flow out. That is, since the flow resistance when passing between the heat transfer plates is made uniform, the fluid as the heat exchange medium flows more uniformly in the shell.

  As described above, the heat exchanger according to the present invention has an excellent effect that the fluid as the heat exchange medium flows uniformly in the shell.

  An exhaust heat power generation apparatus 10 that is a heat power generation apparatus to which a heat exchanger according to an embodiment of the present invention is applied as a low-temperature side heat exchanger 14 will be described with reference to FIGS. First, the overall configuration of the exhaust heat power generator 10 will be described, and then the structure of the low temperature side heat exchanger 14 will be described in detail.

(Configuration of exhaust heat generator)
FIG. 3 shows a schematic overall configuration of the exhaust thermoelectric generator 10 in a front view, and FIG. 4 shows a schematic overall configuration of the exhaust thermoelectric generator 10 in a side view. FIG. 5 is a cross-sectional view taken along line 3-3 in FIG. As shown in these drawings, the exhaust thermoelectric generator 10 is applied to an automobile, and a high temperature side heat exchange unit 12 as a heating unit heated by exhaust gas of an internal combustion engine and cooling cooled by engine cooling water. Provided with a plurality of thermoelectric generators (also referred to as thermoelectric element modules) 16 sandwiched between the low-temperature side heat exchanger 14 as a unit, and the thermoelectric generators 16 correspond to the temperature difference between the high temperature side and the low temperature side It is considered as a power generator that generates electromotive force. This will be specifically described below.

  As shown in FIGS. 3 to 5, the exhaust thermoelectric generator 10 includes a high temperature side housing 18. As shown in FIG. 5, the high temperature side housing 18 is formed in a substantially square cylindrical shape, and square pipes 20 each formed in a substantially square cylindrical shape are disposed at the four corners thereof. Between the square pipes 20 adjacent to each other in the vertical direction or the horizontal direction in the high temperature side housing 18, through holes 18 </ b> A are formed, and these through holes 18 </ b> A are respectively closed by the element contact plate 22 </ b> A of the heat collecting member 22. ing. A plurality of heat collecting fins 22B are erected from each element contact plate 22A, and the heat collection fins 22B enter the high temperature side housing 18 with the element contact plate 22A closing the through hole 18A. The high temperature side housing 18 and each heat collecting member 22 constitute the high temperature side heat exchanging portion 12 so as to surround a high temperature gas introduction pipe 24 described later, and the heat collecting fins 22B standing side of the element contact plate 22A The opposite surface constitutes the outer surface 12A of the high temperature side heat exchange section 12.

  Further, a high temperature gas introduction pipe (exhaust pipe) 24 whose longitudinal direction coincides with the axial direction of the high temperature side housing 18 is disposed at the axial center portion of the high temperature side housing 18. The hot gas introduction pipe 24 is provided with a communication hole 24 </ b> A in its pipe wall, and guides hot exhaust gas introduced from an internal combustion engine (not shown) into the high temperature side housing 18. The communication holes 24A are provided at a plurality of locations (four locations in this embodiment) along the circumferential direction of the hot gas introduction pipe 24 in a radial manner with the heat collecting member 22 side facing.

  Thereby, in the high temperature side housing 18, the four high temperature side heat exchange paths 26 formed between the outer surface of the high temperature gas introduction pipe 24 and each element contact plate 22A are connected to the high temperature side housing 18 (the high temperature gas introduction pipe). 24) along the circumferential direction. The heat collecting fins 22 </ b> B of each heat collecting member 22 are located in the corresponding high temperature side heat exchange paths 26. The exhaust gas introduced into each high temperature side heat exchange path 26 from the high temperature gas introduction pipe 24 passes through the inside of the square pipe 20 after passing through the high temperature side heat exchange path 26 (the muffler device of the automobile). Etc.).

  As shown in FIG. 5, each of the heat collecting elements 22 has an element contact plate 22 </ b> A on the surface opposite to the heat collection fin 22 </ b> B standing side, that is, on the outer surface 12 </ b> A of the high temperature side heat exchange section 12. The high temperature side surface of 16 is in contact. On the other hand, a low temperature side heat exchanger 14 described in detail later is in contact with the surface opposite to the high temperature side surface of each thermoelectric generator 16 formed in a flat plate shape, that is, the low temperature side surface. The low temperature side heat exchanger 14 is provided for each thermoelectric generator 16, and cools the thermoelectric generator 16 by exchanging heat with engine cooling water as a refrigerant passing through each thermoelectric generator 16.

  The thermoelectric generator 16 is configured to generate an electromotive force based on a temperature difference between the high temperature side (exhaust gas) and the low temperature side (engine cooling water) due to, for example, the Seebeck effect. As shown in FIG. 3, one thermoelectric generator 16, the heat collecting member 22 (high temperature side heat exchange path 26) and the low temperature side heat exchanger 14 that are in contact with the thermoelectric generator 16 constitute one power generation unit 28. In addition, as shown in FIG. 5, a plurality of (four in this embodiment) power generation units 28 arranged along the circumferential direction of the high temperature side housing 18 (high temperature side heat exchanging portion 12) have one power generation unit group 30. Is configured. Therefore, in each power generation unit group 30, the four low temperature side heat exchangers 14 are arranged at equal intervals in the circumferential direction of the high temperature side heat exchange unit 12.

  As shown in FIG. 4, in this embodiment, three power generation unit groups 30 are provided along the axial direction of the high temperature side housing 18. In each power generation unit group 30, the thermoelectric generation elements 16 constituting the plurality (four) of power generation units 28 are the heat collecting member 22 and the low temperature side heat exchanger 14 from the outside of each low temperature side heat exchanger 14. It is held by the high temperature side housing 18 by being restrained by a common band-shaped member (not shown) to be wound.

  Further, the power generation unit groups 30 adjacent to each other in the axial direction of the high temperature side housing 18 have the positions of the power generation units 28 (low temperature side heat exchangers 14) in the circumferential direction of the high temperature side housing 18 matched. As a result, as shown in FIG. 4, a plurality of (three in this embodiment) power generation units 28 arranged in a straight line along the axial direction of the high temperature side housing 18 constitute one power generation unit row 32. Yes. In this embodiment, four power generation unit rows 32 are provided along the circumferential direction of the high temperature side housing 18. In each power generation unit row 32, the low temperature side heat exchangers 14 adjacent in the axial direction of the high temperature side housing 18 are connected by a communication pipe 34.

  The exhaust heat power generation apparatus 10 includes a cooling water distribution structure 35 for distributing engine cooling water as a refrigerant to each power generation unit row 32. In this cooling water distribution structure 35, a branch bypass flow path is provided at the upstream end of each low-temperature side heat exchanger 14 located at the uppermost stream (the left end in FIG. 4) in the flow direction of the engine cooling water in each power generation unit row 32. The branch pipe 36 is connected. On the other hand, at the downstream end of each low-temperature side heat exchanger 14 located at the most downstream (right end in FIG. 4) in the flow direction of the engine cooling water in each power generation unit row 32, a merging pipe 38 as a branch bypass flow path is respectively provided. It is connected.

  Further, the branch pipe 36 of each power generation unit row 32 is connected to a common cooling water inlet header 40 as a distribution bypass flow path, and the junction pipe 38 of each power generation unit row 32 is connected to a common cooling water outlet header. 42. The cooling water inlet header 40 is connected to a cooling water introduction pipe 44 as a cooling water introduction section, and the cooling water outlet header 42 is connected to a cooling water discharge pipe 46 as a cooling water outlet section. As shown in FIG. 4, in each power generation unit row 32, the branch pipe 36, the communication pipe 34, and the junction pipe 38 are arranged in a straight line along the axial direction of the high temperature side housing 18. In this embodiment, as shown in FIG. 3, the branch pipe 36, the communication pipe 34, and the junction pipe 38 are connected to the center in the width direction of the low temperature side heat exchanger 14.

  Thereby, in the cooling water distribution structure 35 of the exhaust heat power generator 10, the engine cooling water introduced from the cooling water introduction pipe 44 to the cooling water inlet header 40 is distributed to each branch pipe 36, and the low temperature of each power generation unit row 32 is obtained. The engine cooling water passes through the side heat exchanger 14 (communication pipe 34) linearly, and merges at the cooling water outlet header 42 via each merging pipe 38, and is discharged from the cooling water discharge pipe 46 outside the system (such as a radiator). ) To be discharged. The low temperature side heat exchanger 14 cools the thermoelectric generator 16 in each power generation unit 28 by the flow of the cooling water.

  In this embodiment, as shown in FIG. 3, the cooling water inlet header 40 is a virtual circle (not shown) connecting four branch pipes 36 arranged at equal intervals in the circumferential direction of the high temperature side housing 18 in a front view. ). More specifically, the cooling water inlet header 40 is formed in a substantially C shape in a front view so that two branch pipes 36 adjacent to each other in the circumferential direction among the four branch pipes 36 are located at both ends in the circumferential direction. ing. Thereby, the cooling water inlet header 40 is made into the end, and it is set as the structure by which the annular flow of engine cooling water is not produced | generated inside. In the cooling water distribution structure 35, the cooling water introduction pipe 44 is connected to the central portion in the longitudinal (circumferential) direction of the cooling water inlet header 40 so that the two branch pipes 36 are symmetrically positioned on both sides thereof. Yes.

(Configuration of low-temperature heat exchanger)
As described above, the low temperature side heat exchangers 14 constituting the power generation unit row 32 are connected in series by the communication pipe 34. Each communication pipe 34 communicates with a central portion in the width direction (the circumferential direction of the high temperature side housing 18) of the low temperature side heat exchanger 14 adjacent in the axial direction of the high temperature side housing 18. Specifically, as shown in FIGS. 1A and 1B, each low temperature side heat exchanger 14 is provided with a plurality of cooling (heat radiation) fins 52 as fins in a shell 50. It is configured. The shell 50 of each low temperature side heat exchanger 14 is formed in a substantially rectangular container shape flattened in the radial direction (radial direction) of the high temperature side housing 18.

  Each shell 50 is provided at a refrigerant inlet 54 as a fluid inlet provided at a central portion in the width direction of one end in the axial direction of the high temperature side housing 18 and at a central portion in the width direction at the other end in the axial direction of the high temperature side housing 18. And a refrigerant outlet 56 as a fluid outlet. The refrigerant inlet 54 and the refrigerant outlet 56 are each configured as a cylindrical convex portion.

  As shown in FIGS. 1 and 5, the portion of the shell 50 where the outer surface is in contact with the low temperature side of the thermoelectric generator 16 is a heat transfer wall 58. As shown in FIG. The fins 52 are erected from the inner surface of the heat transfer wall 58. The cooling fins 52 are each formed in a substantially rectangular flat plate shape extending in the axial direction of the high temperature side housing 18 (a direction perpendicular to the width direction of the shell 50), and are parallel to each other and in the width direction of the shell 50. They are arranged at equal intervals. Each cooling fin 52 dissipates heat transferred from the thermoelectric generator 16 through the heat transfer wall 58 to the engine cooling water. The heat exchange area is increased.

  Further, as shown in FIG. 1B, the cooling fins 52 positioned on the outermost side in the width direction of the shell 50 have the same distance from the side wall 60 of the shell 50 as the distance from the adjacent cooling fins 52. Furthermore, as shown in FIG. 1 (A), the end of each cooling fin 52 opposite to the heat transfer wall 58 side and the inner surface of the outer wall 62 facing the heat transfer wall 58 are in contact with almost no gap, Or they are very close. 1A is a front view in which the peripheral wall portion provided with the refrigerant inlet 54 is removed, and FIG. 1B is a view in which the outer wall 62 is removed. In the following description, FIG. For convenience, it is a plan view (the heat transfer wall 58 is on the lower side).

  As described above, in each low temperature side heat exchanger 14, the engine cooling water flowing into the shell 50 from the refrigerant inlet 54 passes (distributed) between the cooling fins 52 and flows out from the refrigerant outlet 56. It has become. Further, between the refrigerant inlet 54 and the cooling fin 52 in the shell 50, there is an inflow side header portion 64 as a diffusion space for diffusing the engine cooling water flowing in from the refrigerant inlet 54 in the width direction of the shell 50. Provided between the cooling fins 52 and the refrigerant outlet 56 in the shell 50 is an outflow side header portion 66 as a merging space for merging the engine cooling water toward the refrigerant outlet 56. Yes.

  As shown in FIGS. 1 (A) and 1 (B), the inflow side header portion 64 in the shell 50 of each low temperature side heat exchanger 14 has a diffusing member 68 constituting the diffusing means in the present invention. It is arranged. The diffusing member 68 is formed in a substantially obtuse isosceles triangle shape that is convex toward the refrigerant inlet 54 side (upstream) in a plan view and whose base is aligned with the width direction of the shell 50. As shown in FIG. 1B, the maximum width Wd of the diffusing member is larger than the inner diameter D, which is the maximum width of the refrigerant inlet 54, and the width Wh of the inflow-side header portion 64 (the inner width of the shell 50). ). Further, as shown in FIG. 1A, the diffusion member 68 has a height Hd smaller than the height Hf of the cooling fin 52 (that is, the distance between the heat transfer wall 58 and the outer wall 62), The end surface is fixed to the inner surface of the heat transfer wall 58. In this embodiment, the height Hd is about half of the height Hf. Note that the diffusion member 68 may be fixed to the outer wall 62.

  Therefore, in each low temperature side heat exchanger 14, the engine coolant that has flowed into the shell 50 from the refrigerant inlet 54 is prevented from going straight by the diffusion member 68 and diffused in the width direction of the shell 50 in the inflow side header portion 64. And a flow component that passes over the diffusion member 68 (on the outer wall 62 side) and mainly passes through the center portion in the width direction of the shell 50. In addition, the arrow suitably shown in FIG.1 (B) shows roughly the macro flow direction (dispersibility) of engine cooling water.

  Next, the operation of the first embodiment will be described.

  In the exhaust heat power generation apparatus 10 configured as described above, when the engine of the automobile is started, the exhaust gas of the engine is introduced into each high temperature side heat exchange path 26, that is, to the high temperature side heat exchange section 12 through the high temperature gas introduction pipe 24. This exhaust gas gives heat (heat exchange) to the element contact plate 22A while being in contact with the heat collecting fins 22B. Thereby, in each power generation unit 28, the high temperature side of the thermoelectric generator 16 is heated. The exhaust gas that has been cooled by the heat exchange and has passed through the high temperature side heat exchanging section 12 is discharged outside the apparatus through the square pipe 20. On the other hand, the engine coolant is circulated in the order of, for example, the low temperature side heat exchanger 14 (shell 50) of each power generation unit 28 of each power generation unit row 32, the engine, and the radiator by the operation of the water pump of the engine. The low temperature side of the thermoelectric generator 16 is cooled via the exchanger 14.

  As described above, the high temperature side of the thermoelectric generation element 16 constituting each power generation unit 28 is heated by effectively using the heat of the exhaust gas, and the low temperature side of each thermoelectric generation element 16 is cooled by the cooling water. A temperature difference between the high and low temperatures of each thermoelectric generator 16 is ensured, and each thermoelectric generator 16 generates an electromotive force based on this temperature difference. That is, in each power generation unit 28, the thermoelectric generator 16 generates power. The generated electric power is stored in a battery or the like that is a storage battery mounted on the automobile (charges the battery).

  Here, in the low temperature side heat exchanger 14 constituting the exhaust thermoelectric generator 10, the diffusion member 68 is disposed in the inflow side header portion 64 in the shell 50, so that engine cooling water flows in the inflow side header portion 64 of the shell 50. It diffuses (distributed) in the width direction and flows substantially uniformly between the plurality of cooling fins 52 and between the cooling fins 52 and the side walls 60 (hereinafter simply referred to as between the fins 52). In particular, since the width Wd of the diffusing member 68 is larger than the inner diameter D of the refrigerant inlet 54, the structure without the diffusing member 68 makes it difficult for the engine coolant to flow between the fins 52 on the end side in the width direction in the shell 50. The engine cooling water can be guided effectively, and the engine cooling water flows more uniformly between the fins 52 as a whole.

  Hereinafter, a specific description will be given by comparison with the comparative example shown in FIG. The heat exchanger 200 according to the comparative example shown in FIG. 16 is configured in exactly the same way as the low temperature side heat exchanger 14 except that the diffusion member 68 is not provided. Parts corresponding to the configuration of the low temperature side heat exchanger 14 in the heat exchanger 200 will be described with the same reference numerals as the low temperature side heat exchanger 14.

  FIG. 2B shows the engine cooling water when the engine cooling water is caused to flow into the shell 50 from the heat exchanger 200 refrigerant inlet 54 and the engine cooling water is caused to flow out of the shell 50 via the refrigerant outlet 56. The numerical-analysis result which shows the flow velocity (flow rate) distribution of is shown typically. From this figure, it can be seen that in the heat exchanger 200, the flow of engine cooling water concentrates in the center portion in the width direction in the shell 50, and the amount of engine cooling water that contacts the cooling fins 52 on the width direction end portion side is small. On the other hand, FIG. 2 (A) schematically shows the flow velocity distribution of the engine cooling water when the engine cooling water flows through the low temperature side heat exchanger 14 under the same conditions as in the analysis of FIG. 2 (B). . From this figure, the diffusion member 68 prevents the flow of engine cooling water from concentrating at the center in the width direction in the shell 50, and the difference in flow rate of engine cooling water between the width direction center and the width direction end ( It can be seen that the flow rate difference is kept small.

  Thus, in the exhaust thermoelectric generator 10 according to the first embodiment, the engine coolant that is the heat exchange medium flows uniformly in the shell 50. Thereby, the heat exchange efficiency of the low temperature side heat exchanger 14 improves. That is, heat can be efficiently removed from the heat transfer wall 58 by the refrigerant having the same temperature and the same flow rate. Therefore, in the exhaust thermoelectric generator 10 to which the low temperature side heat exchanger 14 is applied, the low temperature side of the thermoelectric generator 16 can be satisfactorily cooled by the engine coolant having restrictions on the vehicle operation in terms of temperature and flow rate. The power generation efficiency is improved (the power generation amount is increased).

  Moreover, in the low temperature side heat exchanger 14, since the height Hd of the diffusing member 68 is smaller than the height Hf of the cooling fin 52, the single diffusing member 68 having no cooling water bypass flow path such as a through hole is provided. Thus, it is possible to secure the flow of engine cooling water in the center portion in the width direction of the shell 50.

Next, reference examples not included in the present invention and other embodiments of the present invention will be described. The same parts and portions as those in the first embodiment or the previous configuration are denoted by the same reference numerals as those in the first embodiment or the previous configuration, and the description thereof is omitted.

(First Reference Example )
FIG. 6A shows a low-temperature side heat exchanger 70 according to the first reference example of the present invention in a front view corresponding to FIG. 1A, and FIG. The side heat exchanger 70 is shown in a plan view corresponding to FIG. As shown in these drawings, the low temperature side heat exchanger 70 is provided only in the inflow side header portion 64 in that diffusion portions 72 and 74 are provided in both the inflow side header portion 64 and the outflow side header portion 66. This is different from the first embodiment in which the diffusing member 68 is provided. Further, the low temperature side heat exchanger 70 is different from the first embodiment in that the diffusion part 72 is configured by a pair of diffusion members 72A and 72B and the diffusion part 74 is configured by a pair of diffusion members 74A and 74B. Is different.

  The pair of diffusing members 72A and 72B are formed in such a manner that the diffusing member 68 is divided into two so as to form a bypass channel 72C that widens toward the downstream at the center in the width direction of the shell 50. Are formed symmetrically with respect to an imaginary line (width direction center line) L1 connecting the axis of the refrigerant and the axis of the refrigerant outlet 56. Accordingly, in the pair of diffusion members 72A and 72B, the tapered surfaces facing the upstream side (and the outer side in the width direction) guide the engine coolant to the end portion in the width direction in the shell 50 and face the downstream side (and the inner side in the width direction). The tapered surface (bypass passage 72C road wall) is configured to diffuse the engine coolant passing through the bypass passage 72C in the width direction.

  In addition, the diffusion part 74 is positioned downstream of the cooling fins 52 while the diffusion part 72 guides the engine cooling water directly to the outside in the width direction. The cooling water is diffused in the width direction in the shell 50. The diffusion unit 74 is configured symmetrically to the diffusion unit 72 with respect to an imaginary line (flow direction center line) L2 that equally divides the low-temperature side heat exchanger 70 into two upstream and downstream sides. Therefore, the diffusing portion 74 has a bypass channel 74C that is reduced in width toward the downstream in the center in the width direction between the pair of diffusing members 74A and 74B, and a shell is formed at the bypass channel wall of the bypass channel 74C. The engine coolant that has passed through the central portion in the width direction in 50 is guided to the refrigerant outlet 56, and the engine coolant that has passed through the width direction end portion in the shell 50 is guided to the refrigerant outlet 56 with a tapered surface facing downstream. It is like that.

  The maximum width of the diffusion part 72 and the diffusion part 74, that is, the distance between the width direction outer end of the pair of diffusion members 72A and the width direction outer end part of the diffusion member 72B, and the width direction outer ends of the pair of diffusion members 74A The distance Wd2 from the outer end portion in the width direction of the member 74B is larger than the above-described width Wd and smaller than the width Wh, and further improves the diffusibility of the engine coolant in the width direction outside. It is said that. Further, each of the diffusion members 72A, 72B, 74A, and 74B has a height that is equal to the height of the cooling fin 52, and is configured to prevent the engine cooling water from overflowing.

In the low temperature side heat exchanger 70 demonstrated above, since the spreading | diffusion part 72 is provided in the inflow side header part 64, there exists an effect similar to the low temperature side heat exchanger 14 which concerns on 1st Embodiment fundamentally. . That is, in the low temperature side heat exchanger 70 according to the first reference example , the engine cooling water as the heat exchange medium flows uniformly in the shell 50, and the heat exchange efficiency is improved. Therefore, in the exhaust heat power generator 10 to which the low temperature side heat exchanger 70 is applied, power generation efficiency is improved (power generation amount is increased).

  Moreover, in the low temperature side heat exchanger 70, since the diffusion part 72 is comprised by a pair of diffusion members 72A and 72B which form the bypass flow path 72C in the center part in the width direction, the height of the diffusion part 72 is cooled. In the configuration matched with the height of the fins 52, the flow of engine cooling water at the center in the width direction of the shell 50 can be ensured.

  Furthermore, in the low temperature side heat exchanger 70, the diffusion part 72 and the diffusion part 74, which are respectively formed with respect to the virtual line L1, are provided symmetrically with respect to the virtual line L2, and therefore the virtual line L1 and the virtual line It is configured point-symmetrically with respect to the intersection point X with L2. Therefore, the low-temperature side heat exchanger has the same configuration as the case where it does not reverse even if it is inverted around the intersection X, in other words, the refrigerant inlet 54 side and the refrigerant outlet 56 side (that is, the diffusion portion 72 and the This eliminates the need to distinguish between the diffuser 74 and prevents erroneous assembly.

In the first reference example , the example in which each diffusion portion 72, 74 is configured by a pair of diffusion members 72A, 72B and a pair of diffusion members 74A, 74B is shown, but the present invention is not limited to this. For example, as shown in FIG. 7, the low temperature side heat exchanger 70 has a pair of diffusion part halves 76A and 76B (substantially the same shape as the diffusion members 72A and 72B) instead of one or both of the diffusion parts 72 and 74. May be configured to include a diffusion portion 76 having a bypass channel 76D at the center in the width direction. Further, the connecting portion 76C may be provided on the heat transfer wall 58 side, on the outer wall 62 side, or on both the heat transfer wall 58 side and the outer wall 62 side, and may be separated from the heat transfer wall 58 and the outer wall. May be provided.

( Second reference example )
FIG. 8 (A) shows a low temperature side heat exchanger 80 according to a second reference example of the present invention in a cross-sectional view corresponding to FIG. 1 (A), and FIG. The side heat exchanger 80 is shown in a plan view corresponding to FIG. As shown in these drawings, the low temperature side heat exchanger 80 is configured such that diffusion portions 82 and 84 provided in the inflow side header portion 64 and the outflow side header portion 66 are divided into four in the width direction. This is different from the first reference example .

  Specifically, the diffusing portion 82 disposed in the inflow side header portion 64 is symmetrical with respect to the imaginary line L1 so that the diffusing member 68 is divided into four at three locations including the central portion in the width direction of the shell 50. The pair of diffusion members 82A and the diffusion member 82B located on the outer side in the width direction of the pair of diffusion members 82A are configured. A bypass channel 82C is formed at the center in the width direction of the diffusing portion 82 so as to be sandwiched between the pair of diffusing members 82A and widen downstream, and between the nuclear diffusing member 82A and the adjacent diffusing member 82B. Is formed with a pair of bypass channels 82D that widen toward the downstream.

  Further, the diffusing unit 84 is configured symmetrically with the diffusing unit 82 with respect to the virtual line L2. Therefore, the diffusing section 84 has a pair of diffusing members 84A and 84B, respectively, and a bypass channel 84C is formed between the pair of diffusing members 84A. A bypass channel 84D that is reduced in width toward the downstream is formed between the matching diffusion members 84A and 84B.

  The maximum widths of the diffusing portion 82 and the diffusing portion 84, that is, the distance between the outer ends in the width direction of the pair of diffusing members 82B, and the distance Wd3 between the outer ends in the width direction of the pair of diffusing members 84B are respectively the width Wd2 described above. It is considered equivalent. Further, each of the diffusion members 82A, 82B, 84A, 84B has a height equal to the height of the cooling fin 52, and is configured to prevent the engine cooling water from overflowing.

In the low-temperature side heat exchanger 80 described above, the diffusion unit 72 to the inlet side header 64 is provided, basically the first embodiment, low-temperature heat exchanger according to a first reference example 14,70 Has the same effect as. That is, in the low temperature side heat exchanger 80 according to the second reference example , the engine cooling water as the heat exchange medium flows uniformly in the shell 50, and the heat exchange efficiency is improved. Therefore, in the exhaust heat power generator 10 to which the low temperature side heat exchanger 80 is applied, the power generation efficiency is improved (the amount of power generation is increased).

Further, in the low temperature side heat exchanger 80, each of the pair of diffusion members 82A, in which the diffusion portion 82 forms the bypass flow channel 82C at the central portion in the width direction and forms the bypass flow channel 82D at two positions sandwiching the bypass flow channel 82C, 82B is configured so that the height of the diffusion portion 82 matches the height of the cooling fins 52, while ensuring the flow of engine cooling water in the central portion in the width direction of the shell 50, as a whole. The engine cooling water can flow more uniformly between the cooling fins 52. FIG. 9 schematically shows the flow velocity distribution of the engine cooling water when the engine cooling water is caused to flow through the low temperature side heat exchanger 80 under the same conditions as the analysis of FIGS. 2 (A) and 2 (B). is there.

  Further, in the low-temperature side heat exchanger 80, as in the low-temperature side heat exchanger 70, it is not necessary to distinguish between the refrigerant inlet 54 side and the refrigerant outlet 56 side before the assembly, thus preventing erroneous assembly. Is done.

In the second reference example , each diffusion portion 82 and 84 is configured by each pair of diffusion members 82A and 82B and each pair of diffusion members 84A and 84B. However, the present invention is not limited thereto. For example, similarly to the diffusion part 76 described above, the diffusion part 82 having the three bypass flow paths 82C and 82D is configured by a single member in which each pair of diffusion members 82A and 82B is connected by the connection part. Also good.

(Third reference example)
FIG. 10 (A) shows a low temperature side heat exchanger 90 according to a third reference example of the present invention in a cross-sectional view corresponding to FIG. 1 (A), and FIG. The side heat exchanger 90 is shown in a plan view corresponding to FIG. As shown in these drawings, the low temperature side heat exchanger 90 is different from the first reference example in that diffusion portions 92 and 94 are provided in both the inflow side header portion 64 and the outflow side header portion 66. .

  The diffusing portion 94 has a pair of diffusing members 94A and 94B, and is common to the diffusing portion 74 in that a bypass channel 94C that is reduced in width toward the downstream is formed between them. It differs from the diffusion part 74 in that the upstream-facing surface located on the outer side in the width direction is a tapered surface 94D that also faces the outer side in the width direction. The diffusion portion 94 is configured to reduce the flow resistance of engine cooling water by the tapered surface 94D. On the other hand, the diffusion part 92 is formed symmetrically with the diffusion part 94 with respect to the virtual line L2. Therefore, the diffusing portion 92 has a bypass channel 92C that is widened downstream in the center in the width direction between the pair of diffusing members 92A and 92B, and the shell 50 is formed at the bypass channel wall of the bypass channel 92C. The engine coolant that has passed through the central portion in the width direction is configured to diffuse in the width direction.

  The maximum width of the diffusion portion 92 and the diffusion portion 94, that is, the distance between the width direction outer end of the pair of diffusion members 92A and the width direction outer end portion of the diffusion member 92B, and the width direction outer ends of the pair of diffusion members 94A The distance Wd4 from the outer end portion in the width direction of the member 94B is equal to the above-described width Wd2. Further, each of the diffusion members 92A, 92B, 94A, 94B has a height equal to the height of the cooling fin 52, and is configured not to allow the engine coolant to overflow.

In the low temperature side heat exchanger 90 described above, the diffusion portion 92 is provided in the inflow side header portion 64. Therefore, the low temperature side heat exchanger according to the first embodiment and the first and second reference examples is basically provided. The same effects as those of 14, 70, 80 are achieved. That is, in the low temperature side heat exchanger 90 according to the third reference example , the engine cooling water as the heat exchange medium flows uniformly in the shell 50, and the heat exchange efficiency is improved. Therefore, in the exhaust heat power generator 10 to which the low temperature side heat exchanger 90 is applied, the power generation efficiency is improved (the amount of power generation is increased).

Moreover, in the low temperature side heat exchanger 90, since the diffusion part 92 is composed of a pair of diffusion members 92A and 92B that form a bypass channel 92C in the center in the width direction, the height of the diffusion part 92 is cooled. In the configuration matched with the height of the fins 52, the flow of engine cooling water at the center in the width direction of the shell 50 can be ensured. FIG. 11 schematically shows the flow velocity distribution of the engine cooling water when the engine cooling water flows through the low temperature side heat exchanger 90 under the same conditions as in the analysis of FIGS. 2 (A) and 2 (B). is there.

  Moreover, in the low temperature side heat exchanger 90, the tapered portion 94D is formed in the diffusion portion 94, so that, for example, compared with the low temperature side heat exchanger 70 including the diffusion portion 74 that does not have the tapered surface 94D, the engine The flow resistance of the cooling water is reduced. Further, in the low temperature side heat exchanger 90, similarly to the low temperature side heat exchanger 70, it is not necessary to distinguish between the refrigerant inlet 54 side and the refrigerant outlet 56 side before assembling, thereby preventing erroneous assembly. Is done.

In the third reference example , each diffusion unit 92, 94 is configured by a pair of diffusion members 92A, 92B and a pair of diffusion members 94A, 94B. However, the present invention is not limited to this. For example, similarly to the diffusion unit 76 described above, the diffusion units 92 and 94 may be configured by a single member in which a pair of diffusion members 92A and 92B and a pair of diffusion members 94A and 94B are connected by a connection unit. Further, the diffusing parts 92 and 94 may be divided into four parts in the width direction as in the diffusing parts 82 and 84 (configured by setting a tapered surface 94D on the diffusing parts 82 and 84).

( 4th reference example )
FIG. 12 (A) shows a low temperature side heat exchanger 100 according to a fourth reference example of the present invention in a plan view corresponding to FIG. 1 (B), and FIG. The side heat exchanger 100 is shown in a side sectional view. As shown in these figures, the low-temperature side heat exchanger 100 includes a shell 102 in place of the shell 50, and in that the diffusing member is not disposed in the shell 102, the first embodiment, first to Different from the third reference example .

  The shell 102 has a height with respect to the inflow side header portion 64 so that the engine coolant flows into the inflow side header portion 64 from the inlet 104 provided in the center in the width direction of the inflow side header portion 64 in the outer wall 62. A refrigerant inlet 106 is provided that is offset in the direction (over the entire height of the cooling fin 52). Further, the shell 102 is offset in the height direction with respect to the outflow side header portion 66 so that the engine coolant flows out from the outflow port 108 provided in the center portion in the width direction of the outflow side header portion 66 in the outer wall 62. The refrigerant outlet 110 is provided. The refrigerant outlet 110 is formed symmetrically with the refrigerant inlet 106 with respect to the virtual line L2.

  Therefore, the shell 102 is configured such that it is not necessary to distinguish between the refrigerant inlet 106 and the refrigerant outlet 110 before assembly to the exhaust thermoelectric generator 10. Further, since the refrigerant inlet 106 and the refrigerant outlet 110 are coaxially positioned in the shell 102, the shell 102 and the communication pipe 34 that are adjacent to each other in the axial direction of the high temperature side housing 18 (constitute the same power generation unit row 32). It is set as the structure which can be connected linearly.

  In the shell 102, a portion constituting the inflow side header portion 64 in the heat transfer wall 58 (a portion protruding upstream from the upstream end of each cooling fin 52) is a diffusion portion 112. This diffusing portion 112 has its inner surface (substantially flat surface) blocked by blocking the flow of engine cooling water flowing into the inflow side header portion 64 from the inlet 104 toward the central portion in the width direction of the diffusing portion 112. The engine cooling water flow is diffused in the width direction of the shell 102. Accordingly, the refrigerant inlet 106 (inlet 104) that generates a flow toward the center in the width direction of the engine cooling water diffusion portion 112 corresponds to the “fluid guide portion” in the present invention.

Further, in this reference example , the shell 102 is formed by cutting off the four corners of the rectangle in a plan view in a substantially S shape. For this reason, a part of the cooling fins 52 on the side in the width direction (side close to the side wall 60) is configured such that the longitudinal dimension is reduced toward the outer side in the width direction.

In the low temperature side heat exchanger 100 described above, the engine cooling water that has flowed into the inflow side header portion 64 from the inflow port 104 is blocked by the diffusion portion 112 in the flow toward the center in the width direction of the diffusion portion 112. In the inflow side header portion 64, it diffuses in the width direction of the shell 102 and flows substantially uniformly between the plurality of cooling fins 52. That is, in the low temperature side heat exchanger 100 according to the fourth reference example , since the refrigerant inlet 106 is provided offset in the height direction with respect to the inflow side header portion 64 in the shell 102, the diffusion member 68 and the like are arranged in the shell 102. Without installation, the engine coolant, which is a heat exchange medium, flows uniformly in the shell 102, and the heat exchange efficiency is improved. Therefore, in the exhaust heat power generator 10 to which the low temperature side heat exchanger 100 is applied, the power generation efficiency is improved (the amount of power generation is increased).

  FIG. 13 schematically shows the flow velocity distribution of the engine cooling water when the engine cooling water is passed through the low temperature side heat exchanger 100 under the same conditions as the analysis of FIGS. 2 (A) and 2 (B). is there. From this figure, the diffusion part 112 effectively suppresses the flow of engine cooling water from concentrating in the center in the width direction in the shell 50, and the engine cooling water in the width direction center and the end in the width direction is effectively suppressed. It can be seen that the flow rate difference (flow rate difference) is significantly reduced.

  Further, in the low temperature side heat exchanger 100, similarly to the low temperature side heat exchanger 70 and the like, there is no need to distinguish between the refrigerant inlet 106 side and the refrigerant outlet 110 side before the assembly, which may cause an erroneous assembly. Is prevented.

(Second Embodiment)
FIG. 14 shows a low-temperature heat exchanger 120 according to the second embodiment of the present invention in a plan view corresponding to FIG. As shown in these drawings, the low temperature side heat exchanger 120 is configured by arranging a plurality of cooling fins 122 in the shell 50 in place of the plurality of cooling fins 52. They are different from the first embodiment and the first to fourth reference examples in that they are each elongated in the width direction of the shell 50.

  Each cooling fin 122 is arranged offset in the longitudinal direction with respect to the cooling fin 122 with respect to the adjacent cooling fin 122 so that the overlap amount of the adjacent cooling fins 122 becomes substantially constant. The cooling fins 122 (hereinafter referred to as cooling fins 122 </ b> A when distinguished from other cooling fins 122) disposed closest to the refrigerant inlet 54 distinguish one end from the side wall 60 (hereinafter referred to as other side walls 60). In some cases, a portion between the side wall 60A and the other side wall 60 is referred to as a side wall 60B is a closed portion (seal portion) 130 serving as a first closed portion in which passage of engine coolant is prevented. On the other hand, the cooling fin 122 located closest to the refrigerant outlet 56 (hereinafter referred to as the cooling fin 122B when distinguished from the other cooling fins 122) has an engine cooling water between one end and the side wall 60B. It is set as the obstruction | occlusion part (seal part) 132 as a 2nd obstruction | occlusion part by which passage was prevented. The height of each cooling fin 122 is equal to the height of the cooling fin 52.

  As described above, in the shell 50, the inflow side header portion 124 communicating with the refrigerant inlet 54 is formed on the side wall 60 </ b> B side of each cooling fin 122, and at the refrigerant outlet 56 on the side wall 60 </ b> A side of each cooling fin 122. An outflow side header portion 126 that communicates is formed. The inflow side header portion 124 and the outflow side header portion 126 are each formed in a substantially right triangle shape in plan view. That is, the inflow header portion 124 is configured such that the bypass flow path width becomes narrower as it is separated from the refrigerant inlet 54, and the outflow side header portion 126 is configured such that the bypass flow path width is increased as it is separated from the refrigerant inlet. Thereby, the low temperature side heat exchanger 120 has a configuration in which the flow resistances of a plurality of flow paths passing between different cooling fins 122 are substantially equal.

  In this embodiment, the other end of the cooling fin 122 is located closer to the side wall 60B than the end of the side wall 60B of the refrigerant inlet 54, and the other end of the cooling fin 122B is the refrigerant. It is located closer to the side wall 60A than the end of the outlet 56 on the side wall 60A side. Furthermore, the low temperature side heat exchanger 120 is configured point-symmetrically with respect to the intersection X between the virtual line L1 and the virtual line L2.

  In the low temperature side heat exchanger 120 described above, the engine cooling water flowing into the inflow side header portion 124 from the refrigerant inlet 54 is dispersed between the cooling fins 122 while changing the flow direction, and between the cooling fins 122. Pass through. The engine coolant that has passed between the cooling fins 122 merges at the outflow side header portion 126 and is discharged from the refrigerant outlet 56. As described above, the low temperature side heat exchanger 120 has a structure in which the flow direction of the engine cooling changes when it is distributed between the cooling fins 122 from the inflow side header portion 124 (in this embodiment, changes to substantially right angle). In other words, in other words, the engine cooling water diffused in the longitudinal direction of the inflow-side header portion 124 passes through the cooling fins 122, so that the engine cooling water flows substantially uniformly between the cooling fins 52. , Heat exchange efficiency is improved. Therefore, in the exhaust heat power generator 10 to which the low temperature side heat exchanger 120 is applied, power generation efficiency is improved (power generation amount is increased).

  In particular, in the low temperature side heat exchanger 120, the cooling fins 122 are offset and arranged so that the flow resistance difference when passing between the cooling fins 122 can be reduced. It flows between the cooling fins 52 substantially uniformly. FIG. 15 schematically shows the flow velocity distribution of the engine cooling water when the engine cooling water is caused to flow through the low temperature side heat exchanger 120 under the same conditions as in the analysis of FIGS. 2 (A) and 2 (B). is there. From this figure, the diffusion portion 112 effectively suppresses the flow of engine cooling water from concentrating on a specific portion in the shell 50, and the flow speed of the engine cooling water at the width direction center portion and the width direction end portion side. It can be seen that the difference (flow rate difference) can be significantly reduced.

  Further, in the low temperature side heat exchanger 120, it is not necessary to distinguish between the refrigerant inlet 106 side and the refrigerant outlet 110 side before the assembly, similarly to the low temperature side heat exchanger 70 and the like. Is prevented.

In each of the above embodiments and each reference example , the heat exchanger in the present invention is used for cooling the thermoelectric generator 16 in the postcard thermoelectric generator 10. However, the present invention is not limited to this. It may be applied to any use.

It is a figure which shows the low temperature side heat exchanger which concerns on the 1st Embodiment of this invention, Comprising: (A) is the front view which removed the wall of the shell, (B) is the top view which removed the outer wall is there. (A) is a schematic diagram which shows the result of having simulated the flow velocity distribution of the engine cooling water which passes the low temperature side heat exchanger which concerns on the 1st Embodiment of this invention, (B) passes the heat exchanger which concerns on a comparative example. It is a schematic diagram which shows the result of having simulated the flow velocity distribution of the engine cooling water. 1 is a front view showing a schematic overall configuration of an exhaust heat power generator according to a first embodiment of the present invention. 1 is a side view of an exhaust heat power generator according to a first embodiment of the present invention. FIG. 5 is a cross-sectional view taken along line 3-3 in FIG. 4. It is a figure which shows the low temperature side heat exchanger which concerns on the 1st reference example of this invention, Comprising: (A) is the front view which removed a part of shell wall, (B) is the top view which removed the outer wall. . It is the front view which removed the wall of the shell which shows the modification of the diffusion member which comprises the low temperature side heat exchanger which concerns on the 1st reference example of this invention. It is a figure which shows the low temperature side heat exchanger which concerns on the 2nd reference example of this invention, Comprising: (A) is the front view which removed the wall of the shell, (B) is the top view which removed the outer wall. . It is a schematic diagram which shows the result of having simulated the flow velocity distribution of the engine cooling water which passes the low temperature side heat exchanger which concerns on the 2nd reference example of this invention. It is a figure which shows the low temperature side heat exchanger which concerns on the 3rd reference example of this invention, Comprising: (A) is the front view which removed a part of shell wall, (B) is the top view which removed the outer wall. . It is a schematic diagram which shows the result of having simulated the flow rate distribution of the engine cooling water which passes the low temperature side heat exchanger which concerns on the 3rd reference example of this invention. It is a figure which shows the low temperature side heat exchanger which concerns on the 4th reference example of this invention, Comprising: (A) is the top view which removed the outer wall, (B) is an outer side sectional view. It is a schematic diagram which shows the result of having simulated the flow velocity distribution of the engine cooling water which passes the low temperature side heat exchanger which concerns on the 4th reference example of this invention. It is the top view which removed the outer wall which shows the low temperature side heat exchanger which concerns on the 2nd Embodiment of this invention. It is a schematic diagram which shows the result of having simulated the flow velocity distribution of the engine cooling water which passes the low temperature side heat exchanger which concerns on the 2nd Embodiment of this invention. It is a figure which shows the heat exchanger which concerns on a comparative example, Comprising: (A) is the front view which removed a part of shell wall, (B) is the top view which removed the outer wall.

Explanation of symbols

14 Low-temperature side heat exchanger (heat exchanger)
50 shell 52 cooling fin (fin)
54 Refrigerant inlet (fluid inlet)
56 Refrigerant outlet (fluid outlet)
58 heat transfer wall 60A side wall 60B side wall 62 outer wall (wall portion 9 facing the heat transfer wall)
64 Inflow header section (between fluid inlet in shell and one end of plural fins)
68 Diffusion member (Diffusion means)
1 20 Low temperature side heat exchanger
122 Cooling fin (fin)
130 Blocking part (first blocking part)
132 Blocking part (second blocking part)

Claims (4)

A heat exchanger for exchanging heat between a fluid passing through a shell and a substance in contact with an outer surface of a heat transfer wall of the shell,
A fluid inlet provided at a central portion in the width direction on one end side of the shell;
A fluid outlet provided at the center in the width direction on the other end of the shell;
A plurality of fins, each standing upright from the heat transfer wall, arranged in parallel to each other in the shell so that one end thereof is located on one end side of the shell and the other end is located on the other end side of the shell When,
A diffusion means provided between the fluid inlet in the shell and one end of the fin, for diffusing a fluid flow in the width direction of the shell;
Equipped with a,
The diffusion means is a diffusion member in which an end portion in the width direction of the shell is located outside a width direction end portion of the fluid inlet or the fluid outlet,
And the said diffusion member is a heat exchanger with which the height along the standing direction of each said fin is made smaller than the height of this fin . The heat exchanger according to claim 1, wherein the diffusion member is formed in a tapered shape that is convex toward the fluid inlet side . A heat exchanger for exchanging heat between a fluid passing through a shell and a substance in contact with an outer surface of a heat transfer wall of the shell,
A fluid inlet provided at a central portion in the width direction on one end side of the shell;
A fluid outlet provided at the center in the width direction on the other end of the shell;
Each of them is erected from the heat transfer wall, and is parallel to each other in the shell so that one end thereof is located on one side wall side in the width direction of the shell and the other end is located on the other side wall side in the width direction of the shell. A plurality of fins arranged in
A first closing portion that closes between one end of the fin and the one side wall; and the other end of the fin and the other side wall that are located closer to the fluid outlet than the one fin. A second closing part that closes the gap;
With heat exchanger. The fins are offset from each other so that a distance between one end and the one side wall is large and a distance between the other end and the other side wall is narrow with respect to the fin adjacent to the fluid inlet side. the heat exchanger of claim 3, wherein being.

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