JP5295737B2 - Plate fin heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a plate fin type heat exchanger capable of suppressing the generation of large thermal stress in a joint and a core around the joint at the end of a header tank and preventing deformation and breakage. <P>SOLUTION: The heat exchanger includes: a core 8 in which high temperature fluid passages and low temperature fluid passages are alternately stacked; and inlet-side and outlet-side header tanks 9a, 9b jointed to inlets and outlets of the low temperature fluid passages opened on lateral faces of the core. The ends of the header tanks have round shapes and the inlets and outlets of the fluid passages are opened only in the header tanks. A configuration for arranging a passage different from the high temperature and low temperature fluid passages in a core corresponding to the ends of the header tanks including the round ends, arranging the other fluid passage with no inlet and outlet opened in the header tanks or narrowing the width of the inlet and outlet of the fluid passage toward tips of the header tanks can be adopted. <P>COPYRIGHT: (C)2010,JPO&amp;INPIT

Description

  The present invention relates to a plate fin heat exchanger used in a wide range of industrial fields. More specifically, the present invention relates to a heat exchanger main body (hereinafter referred to as “core” in which passages through which a high-temperature fluid and a low-temperature fluid flow are alternately arranged. It is related with the plate fin type heat exchanger which can prevent generation | occurrence | production of the big thermal stress in the junction part (root) of the header tank attached to "", and its peripheral core part.

  Plate fin type heat exchanger is a heat exchanger in which a passage for circulating a high-temperature fluid and a passage for circulating a low-temperature fluid are alternately stacked, and is a small and light heat exchanger with excellent heat exchange efficiency. It is used in machinery, railway vehicles, power equipment, and a wide range of other industrial fields.

  FIG. 1 is a perspective view showing a structural example of a plate fin type heat exchanger. The heat exchanger 1 includes a core in which a high-temperature fluid passage 3 for circulating a high-temperature fluid (for example, combustion exhaust gas) and a low-temperature fluid passage 4 for circulating a low-temperature fluid (for example, cooling air) are alternately stacked. 2 and header tanks 5a and 5b joined to the side surface of the core 2.

  The high-temperature fluid passage 3 and the low-temperature fluid passage 4 are partitioned by a partition plate called a tube plate (not shown), and the fluid passages 3 and 4 have a corrugated type for promoting heat transfer and various shapes. The fin 7 is provided. Although not clearly shown in FIG. 1, a side bar is provided for keeping the space between the tube plates and sealing the flow path. For example, in FIG. 1, the side bar is located on the entire right side surface on the front side of the core 2 (except for the joint portion of the header tank 5 a) or on the left side surface on the front side of the core 2. Is provided.

  In FIG. 1, the high temperature fluid H passes through the high temperature fluid passage 3 from the left side surface on the front side of the core 2 to the back side, and the low temperature fluid L is input header attached to the right side surface on the front side of the core 2. It is supplied from the tank 5 a, passes through the low temperature fluid passage 4, and is discharged from the outlet header tank 5 b attached to the left side surface on the back side of the core 2. Thereby, heat exchange is performed with high efficiency between both fluids.

  FIGS. 2A and 2B are diagrams for explaining the configuration of the fluid passage in the core structure of the plate fin heat exchanger shown in FIG. 1. FIG. 2A shows the configuration of the low-temperature fluid passage 4, and FIG. The structure of is shown.

  As shown in FIG. 2A, the low-temperature fluid passage 4 includes an inlet-side distributor portion 4a, a main fin portion 4b, and an outlet-side distributor portion 4c. The low-temperature fluid L supplied from the inlet-side header tank 5a through the nozzle 6a passes through the inlet-side distributor portion 4a and is arranged in parallel with the main fin portion 3b of the high-temperature fluid passage 3 shown in FIG. The main fin portion 4b is distributed. Thereafter, the low temperature fluid L undergoes heat exchange with the high temperature fluid H in the process of passing through the main fin portion 4b, and is discharged from the outlet header tank 5b and the nozzle 6b via the outlet distributor portion 4c. . That is, the distributor portions 4a and 4c are opened on the side surface of the core to form the inlet and outlet of the cryogenic fluid passage 4, respectively, and the header tanks 5a and 5b are joined so as to cover the entire area of the inlet and outlet.

  On the other hand, as shown in FIG. 2B, the high temperature fluid H is immediately supplied from the core entry side 3a to the main fin portion 3b, and heat exchange is performed with the low temperature fluid L, and then the core exit side 3c. Discharged from.

  In the plate fin heat exchanger 1 configured in this way, the cross section of the inlet and outlet of the cryogenic fluid passage 4 is the same rectangle, so the shape of the joining surface of the header tank joined thereto is also rectangular. is there. Therefore, when a large temperature difference occurs between the core and the header tank, or when a large temperature difference occurs around the header tank joint (base), the end of the header tank (header tank portion close to the joint) or A large thermal stress is generated in the surrounding core portion. In particular, at the end portion of the header tank, stress concentrates on the corner portion and a high thermal stress is generated, so that the heat exchanger may be deformed or damaged.

  In order to cope with this problem, for example, Patent Document 1 discloses a plate fin type air preheater (a direction in which air is orthogonal to the exhaust gas passage) used for heat exchange between exhaust gas and air of a gas turbine or a high-temperature fuel cell. After being formed in parallel flow with exhaust gas and discharged in the orthogonal direction, the inlet distributor or outlet distributor of the air passage is separated from the inlet end of the exhaust passage by a predetermined distance in the gas flow direction. An air preheater (heat exchanger) is described that is stacked in position (in other words, inside the heat exchanger).

  According to this air preheater, a large temperature gradient generated at the inlet end of the exhaust gas passage and at the end of the heat exchanger and the header tank is suppressed without the need for high-grade heat-resistant materials and complicated structures. It can be reduced. However, as long as there is a corner at the end of the header tank, thermal stress concentrates on that portion, so the technique described in this document is not always sufficient as a countermeasure against thermal stress. Further, when the air passage distributor is provided inside the heat exchanger as in the air preheater described in the same document, the portion functioning as the heat exchanger is reduced accordingly. In order to maintain the heat exchange capacity, the inlet end of the exhaust gas passage must be provided outside, and the heat exchanger becomes large as a whole.

JP 2008-39227 A

  The present invention has been made in view of the problem of generation of a large thermal stress in the local portion of such a plate fin type heat exchanger, and in particular, at the end of the header tank, a header portion or a joint portion close to the joint portion. An object of the present invention is to provide a plate fin type heat exchanger capable of suppressing the occurrence of large thermal stress in the peripheral core portion and preventing deformation and breakage.

  In order to solve the above-mentioned problems, the inventors of the present invention do not make the cross-sectional shape of the header tank attached to the inlet and outlet of the high-temperature fluid passage or the cryogenic fluid passage into a rectangular shape according to the shape of the core, but end portions. A method for coping with a circular shape or an elliptical shape (that is, a shape with a large radius of curvature R) was studied. As a result, it was found by thermal stress analysis that the thermal stress in the tube plate (air side) near the header tank joint and the end of the header tank is greatly reduced.

  However, for example, when a rectangular header tank joined to the inlet of the cryogenic fluid passage is replaced with a header tank having a large rounded end, a part of the inlet of the cryogenic fluid passage is detached from the header tank (in other words, the header tank As will be described later, the thermal efficiency is lowered. This can be dealt with by adopting, for example, the following configurations (a) to (c).

(A) The fluid passage including the inlet and the outlet coming off from the header tank is replaced with a passage in which the inlet and the outlet are not opened in the header tank and different from the high temperature fluid passage and the low temperature fluid passage.
(B) The fluid passage including the inlet and the outlet coming out of the header tank is replaced with the other fluid passage where the inlet and the outlet are not opened in the header tank.
(C) The width of the inlet and outlet of the fluid passage is narrowed as approaching the tip of the header tank in accordance with the contour of the end of the header tank having a large rounded end.

  The present invention has been made on the basis of such examination results, and is summarized in the following plate fin type heat exchanger.

That is, any one of a core in which a high-temperature fluid passage that circulates a high-temperature fluid and a low-temperature fluid passage that circulates a low-temperature fluid are alternately stacked, and a high-temperature fluid passage and a low-temperature fluid passage that are open on a side surface of the core. A plate fin type heat exchanger having an inlet header tank and an outlet header tank respectively joined to one or both of the inlet and outlet, and at least one of the inlet header tank and the outlet header tank The header tank has a shape with rounded ends at the joint surface , and an inlet and an outlet of a fluid passage to which the header tank is joined are opened only in the header tank. It is a heat exchanger.

  The above-mentioned “inlet or outlet of one or both of a high-temperature fluid passage and a low-temperature fluid passage that are open on the side surface of the core” refers to an inlet that sends these fluids from the inlet header tank to the fluid passage in the core. And an outlet for discharging these fluids from the core fluid passage to the outlet header tank. That is, these inlets and outlets are portions where side bars are not provided on the side surface of the core.

  In the plate fin type heat exchanger of the present invention, the core portion corresponding to the end portion of the header tank having a rounded end portion is a passage where the inlet and the outlet are not opened in the header tank. Therefore, an embodiment (Embodiment 1) in which a passage different from the high-temperature fluid passage and the low-temperature fluid passage can be employed.

  Further, in the plate fin heat exchanger of the present invention, the inlet and outlet are not opened in the header tank at the core portion corresponding to the end of the header tank having a rounded end. Embodiment (Embodiment 2) which arrange | positions the other fluid channel | path can be taken.

Furthermore, in the plate fin type heat exchanger of the present invention, the inlet and outlet of the fluid passage are closed in the heat exchanger main body portion corresponding to the end of the header tank having a rounded end. It is also possible to adopt an embodiment in which the inlet and outlet of the fluid passage are opened only in the header tank.
In this embodiment, the fluid passage in which the inlet and the outlet are closed is closed so that the width of the inlet and the outlet of the fluid passage becomes narrower as the end of the end of the joint surface of the header tank is approached. The embodiment (Embodiment 3) can also be adopted.

  In the first to third embodiments, the “end portion of the header tank having a rounded shape” is the end portion of the header tank, and the joint portion is a round portion (hereinafter simply referred to as “header tank”). Also called “end of”.) For example, in FIG. 4 shown later, it is a portion that covers from the lower end of the header tank to the fluid passage of the fifth layer (a pair of the high temperature fluid passage and the low temperature fluid passage constitutes one layer). In addition, the “core portion corresponding to the end portion” refers to all fluid passage (layer) portions including the surface to which the end portion of the header tank is joined. In FIG. 4, it refers to the core portion from the lower end of the core to the fifth-layer fluid passage.

  If the plate fin type heat exchanger of the present invention is used, even if a temperature difference occurs between the core and the header tank, at the end of the header tank, the header portion close to the joint portion or the core around the joint portion It can suppress that a high thermal stress concentrates on a part and can generate | occur | produce a deformation | transformation and a failure | damage of a heat exchanger. Moreover, the plate fin type heat exchanger of the present invention does not need to provide a fluid passage distributor inside the heat exchanger as in the heat exchanger described in Patent Document 1, and serves as a heat exchanger. The function does not decrease and does not increase as a whole.

  As described above, the plate fin heat exchanger of the present invention has a core in which a high-temperature fluid passage for circulating a high-temperature fluid and a low-temperature fluid passage for circulating a low-temperature fluid are alternately stacked and opened on a side surface of the core. It is based on a plate fin heat exchanger having an inlet header tank and an outlet header tank respectively joined to the inlet and outlet of either or both of the hot fluid passage and the cold fluid passage The end of at least one of the inlet header tank and the outlet header tank has a rounded shape, and the inlet and outlet of the fluid passage to which the header tank is joined are the header. It is characterized by opening only in the tank.

  FIG. 3 is a diagram showing a schematic configuration example of the plate fin heat exchanger of the present invention, where FIG. 3 (a) is a front view, FIG. 3 (b) is a side view, and FIG. 3 (c) is a top view. As shown in FIG. 3, the heat exchanger of the present invention has a core 8 and header tanks 9a and 9b having both ends rounded in this example. Nozzles 10a and 10b are attached to the header tanks 9a and 9b, respectively.

  The inlets and outlets of the cryogenic fluid passages are opened at portions where the header tanks 9a and 9b are attached, that is, the side surfaces of the core, and the cryogenic fluid L is supplied into the core 8 from the header tank 9a via the nozzle 10a. The low-temperature fluid L passes through the inlet-side distributor portion 11a indicated by a broken line in FIG. 3C, and heat exchange is performed with the high-temperature fluid H at the main fin portion 11b. It is discharged from the header tank 9b and the nozzle 10b through the nozzle portion 11c.

  Although not explicitly shown in FIG. 3, the inlet and outlet of the cryogenic fluid passage are opened only in the header tanks 9a and 9b.

  FIG. 4 is a diagram including a partial cross-section in which the end of the header tank 9a in FIG. 3B is enlarged, and is a diagram illustrating a configuration of a heat exchanger according to a third embodiment to be described later. A header tank 9a having a rounded end is indicated by a thick solid line. For comparison, a conventional rectangular header tank is shown by a thick broken line. A portion where the corrugated fins 12 for heat transfer promotion are provided is an opening, and constitutes an inlet to the distributor 11a.

  The low-temperature fluid supplied from the header tank 9a is guided into the core through the distributor 11a from the open inlet. The hot fluid passes through the passage 13 from left to right in FIG. Of each passage of the cryogenic fluid, a side bar is provided in a portion other than the opening (a portion denoted by reference numeral 11s in FIG. 4). In FIG. 4, a solid portion is a portion that was an opening when a conventional rectangular header tank is attached, and a side bar is provided in the heat exchanger of the present invention.

  As shown in FIG. 4, in the heat exchanger of the present invention, the inlet of the cryogenic fluid passage (inlet to the distributor section 11a) is opened only in the header tank 9a. The same applies to the outlet of the cryogenic fluid passage.

  The reason why the end portion of the header tank is rounded in the plate fin heat exchanger of the present invention is to suppress the generation of large thermal stress in the header portion and the core portion around the joint portion. When a conventional header tank with a rectangular joint surface is used, if a large temperature difference occurs around the joint at the end of the header tank, stress is concentrated especially at the corners of the header tank. A large thermal stress is generated in the header portion near the joint and the core portion around the joint. By rounding the end of the header tank, as shown in the examples described later, the stress concentration is relaxed and the thermal stress is greatly reduced.

  There is no particular limitation on the round shape formed at the end of the header tank. The effect is recognized only by giving a slight roundness, but for example, a round shape having a large radius of curvature R such as a circular shape or an elliptical shape has a great effect.

  As illustrated in FIG. 3, the roundness of the end portion of the header tank is preferably formed at both end portions of the inlet header tank and the outlet header tank. You may form in the both ends. Further, when a large thermal stress is generated not at both ends but at one end, for example, only that end may be rounded.

  In the plate fin heat exchanger of the present invention, the inlet and the outlet of the fluid passage to which the header tank having a round shape is joined are opened only in the header tank as described below. This is desirable for maintaining good thermal efficiency, and is also necessary from the viewpoint of safety.

  In the plate fin type heat exchanger of the present invention, in order to change the cross-sectional shape of the header tank attached to the core from a rectangle to a shape with a rounded end, for example, as shown by the filled portion in FIG. An opening is created that will not be contained within the header tank. If they are left open, the heat energy held by the high-temperature fluid is wasted for heat exchange with the low-temperature fluid in the flow path connected to the opening. Moreover, since the said opening is open | released by external air, when the fluid with the high temperature in the flow path connected to an opening is discharge | released in external air, an unexpected situation may be caused.

  In the first to third embodiments, the countermeasures are specifically designed so that the inlet and the outlet of the fluid passage to which the header tank having a rounded end is joined only open in the header tank. This is a heat exchanger.

  In Embodiment 1, in the plate fin type heat exchanger of the present invention, an inlet and an outlet are opened in the header tank in a core portion corresponding to the end of the header tank having a rounded end. This is a heat exchanger in which a passage different from the hot fluid passage and the cold fluid passage is disposed.

  When assembling the core, the passages (layers) through which the high-temperature fluid flows and the passages (layers) through which the low-temperature fluid flows are alternately stacked. At that time, for efficient production, the core is divided into several “unit cores”, assembled and brazed for the unit cores, and the necessary number of unit cores are stacked to form a heat exchanger. A method of forming a core is adopted.

  In the heat exchanger shown in FIG. 3, 14-stage unit cores 8a (see FIGS. 3A and 3B) are stacked to form a core 8.

  In the heat exchanger according to the first embodiment, when the unit cores 8a are stacked, the unit cores used for the other parts of the header tank 9a having the rounded end parts corresponding to the end parts. A unit core different from 8a is used. This unit core does not have an opening at a portion corresponding to the end of the header tank 9a, and is not provided with an opening for supplying or discharging a high-temperature fluid. That is, a unit core in which another passage that does not function as a high-temperature fluid passage and a low-temperature fluid passage is stacked and used at a portion corresponding to the end of the header tank 9a.

  As described above, in the heat exchanger according to the first embodiment, the unit core corresponding to the end of the header tank does not participate in the heat exchange, but the inlet and outlet of both the high temperature fluid passage and the low temperature fluid passage are the header tank. Since it opens only inside, good thermal efficiency is maintained and safety is ensured.

  In the above description, it is assumed that the unit core is used. Of course, the above-mentioned countermeasure is not applied to an integrated core that is not divided into unit cores, but is assembled by alternately stacking high temperature fluid paths and low temperature fluid paths. May be taken. In that case, depending on the thickness of the core portion corresponding to the end portion of the header tank having a rounded end portion (that is, the number of fluid passages (layers)), Arrange different passages (layers).

  The great advantage of the heat exchanger of this embodiment 1 is that it is not necessary to add special modifications to the core itself, and when assembling the core, the type of unit core to be used at the portion corresponding to the end of the header tank, Or when the integral type core which is not divided | segmented into a unit core is used, it exists in the point which only needs to change the channel | path (layer) to arrange | position.

  Embodiment 2 is a heat exchange in which the other fluid passage in which the inlet and the outlet are not opened in the header tank is arranged in the core portion corresponding to the end of the header tank having a rounded end. It is a vessel. For example, when the inlet and outlet of the low temperature fluid flow path are opened in the header tank, the other fluid passage corresponds to the high temperature fluid passage.

  In the heat exchanger according to the second embodiment, as in the heat exchanger according to the first embodiment, the unit core used for the other parts as the unit core corresponding to the end of the header tank when assembling the core, Uses different unit cores. This unit core is the same as the heat exchanger of Embodiment 1 except that it does not have an opening at the portion corresponding to the end of the header tank, but the other fluid whose inlet and outlet are not open in the header tank. In this configuration, passages (in the above example, high-temperature fluid passages) are stacked. Here, the fluid flowing in the other fluid passage (in the above example, the high temperature fluid) passes without exchanging heat with the fluid flowing in the one fluid passage (in the above example, the low temperature fluid). Note that this measure may be taken when an integrated core is used.

  Also in the heat exchanger of the second embodiment, since the inlet and outlet of the high temperature fluid passage and the low temperature fluid passage are opened only in the header tank, good thermal efficiency is maintained and safety is also ensured. In addition, there is an advantage that, when the core is assembled, the type of unit core to be used, or, in the case of an integral core, only the passages (layers) to be stacked and arranged need to be changed.

In the plate fin type heat exchanger of the present invention, the inlet and outlet of the fluid passage are closed in the heat exchanger main body portion corresponding to the end of the header tank having a rounded end. It is also possible to adopt an embodiment in which the inlet and outlet of the fluid passage are opened only in the header tank.
In the third embodiment, the fluid passage in which the inlet and the outlet are closed in the above embodiment is closed so that the width of the inlet and the outlet of the fluid passage is narrowed as the end of the end of the joint surface of the header tank is approached. It is a heat exchanger.

  In the heat exchanger of the third embodiment, the core portion corresponding to the end portion of the header tank has the structure shown in FIG. As shown in the figure, the passage of the cryogenic fluid is narrowed sequentially from both sides in accordance with the contour of the end of the header tank from the lowermost passage to the fourth passage upward. In FIG. 4, a solid portion is a portion closed by a side bar to narrow the width of the entrance.

  Also in this heat exchanger, since the inlet and outlet of the cryogenic fluid passage are arranged in the header tank, good thermal efficiency is maintained and safety is also ensured.

  The header tank having a rounded end is not limited to the vertical type shown in FIG. In a heat exchanger with a low height that matches the actual conditions of use, it is possible to attach a horizontal header tank.

  FIG. 5 is a front view showing another schematic configuration example of the plate fin heat exchanger of the present invention. As shown in FIG. 5, header tanks 15a and 15b having both ends rounded are joined to the core 14 of the heat exchanger. Nozzles 16a and 16b for supplying or discharging a low-temperature fluid are attached to the header tanks 15a and 15b. As described above, the inlet and outlet (opening) of the cryogenic fluid passage are opened only in the header tank.

  In the plate fin heat exchanger of the present invention described above, even in the case where a temperature difference occurs between the core and the header tank, at the end of the header tank, the header portion near the joint portion or the core portion around the joint portion. Stress concentration can be relaxed. Thereby, generation | occurrence | production of a big thermal stress can be suppressed and generation | occurrence | production of a deformation | transformation and a failure | damage of a heat exchanger can be prevented.

  FIG. 3 illustrates the case where the cryogenic fluid is supplied from the header tank, the header tank side becomes low temperature, and the core side becomes high temperature. However, in the heat exchanger of the present invention, the header tank is at the inlet of the high temperature fluid passage. Even if it is attached to the outlet and the header tank side becomes high temperature and the core side becomes low temperature, the same effect can be obtained.

  Plate fin type heat exchanger (hereinafter referred to as “square header mounting structure”) with a conventional rectangular header tank, and a plate fin type with a rounded header tank attached to the end of the present invention Using an analysis model of a heat exchanger (hereinafter referred to as “circular header mounting structure”), thermal stress analysis was performed assuming a state immediately after starting the heat exchanger. The shape of the analysis model is a heat exchanger in which the horizontal header tank illustrated in FIG. 5 is attached to the outlet of the cryogenic fluid passage. In this case, the high temperature fluid is combustion exhaust gas, and the low temperature fluid is air.

  FIG. 6 is a perspective view showing an appearance of an analysis model used for thermal stress analysis and measurement points of generated stress. (A) and (b) show the schematic appearance of the analytical model, and (c) and (d) show the measurement points of the generated stress in the analytical model of the conventional corner header mounting structure. ) And (f) respectively show the measurement points of the generated stress in the analytical model of the circular header mounting structure of the present invention. This analysis model has a core 17 and a rectangular header tank 18 or a rounded header tank 19.

  Table 1 shows, as an example of the thermal stress analysis result, a comparison result of the generated stress in the conventional square header mounting structure and the circular header mounting structure of the present invention.

  In Table 1, the measurement points of the generated stress are (i) spacer bar (exhaust gas inlet), (ii) tube plate (air side), and (iii) header tank (core joint). (Iii) indicates the header portion near the joint. The tube plate is a partition plate between the exhaust gas passage (high temperature fluid passage) and the air passage (low temperature fluid passage), and the spacer bar is a member provided to secure a gap between the laminated passages. In addition, the generated stress is indicated as 1 (reference) in (i): spacer bar (exhaust gas inlet) of the conventional square header mounting structure.

  In FIG. 6C to FIG. 6F, the measurement points are indicated by the reference numerals (i) to (iii).

  As shown in Table 1, by changing the shape of the header tank from the square header mounting structure to the circular header mounting structure, the tube plate (air side) near the header tank joint (measurement point (ii)) and the header tank It was confirmed that the stress at (core junction) (measurement point (iii)) was greatly reduced.

  The plate fin type heat exchanger of the present invention has a rounded shape at the end of the header tank. If this heat exchanger is used, even if a temperature difference occurs between the core and the header tank. The occurrence of high thermal stress at the end of the header tank and its surrounding core can be suppressed, and deformation and breakage of the heat exchanger can be prevented.

  Therefore, the plate fin heat exchanger of the present invention can be effectively used in railway vehicles, electric power facilities, and other industrial fields covering a wide range.

It is a perspective view which shows the structural example of a plate fin type heat exchanger. It is a figure explaining the structure of the fluid passage in the core structure of a plate fin type heat exchanger, The figure (a) is a figure which shows the structure of a low temperature fluid path, (b) is a figure which shows the structure of a high temperature fluid path. It is a figure which shows the schematic structural example of the plate fin type heat exchanger of this invention, The figure (a) is a front view, (b) is a side view, (c) is a top view. It is the front view containing the partial cross section which expanded and showed typically the edge part of the header tank in FIG.3 (b). It is a front view which shows the other schematic structural example of the plate fin type heat exchanger of this invention. It is a perspective view which shows the external appearance of the analysis model used for the thermal stress analysis, and the measurement point of generated stress.

Explanation of symbols

1: heat exchanger, 2: core, 3: hot fluid passage, 4: cold fluid passage,
4a: Distributor part on the entry side, 4b: Main fin part,
4c: Distributor part on the delivery side, 5a, 5b: Header tank,
6a, 6b: nozzle, 7: fin, 8: core,
9a, 9b: header tank, 10a, 10b: nozzle,
11a: Distributor part on the entry side, 11b: Main fin part,
11c: Distributor part on the exit side, 12: Fin, 13: Passage,
14: Core, 15a, 15b: Header tank,
16a, 16b: nozzle, 17: core,
18: Rectangular header tank 19: Header tank with rounded end

Claims (5)

A heat exchanger main body in which a high-temperature fluid passage for circulating a high-temperature fluid and a low-temperature fluid passage for circulating a low-temperature fluid are alternately stacked, and a high-temperature fluid passage and a low-temperature fluid passage that are open on a side surface of the heat exchanger main body A plate fin type heat exchanger having an inlet header tank and an outlet header tank respectively joined to one or both of the inlet and outlet,
At least one of the inlet header tank and the outlet header tank has a rounded end at the joint surface ,
A plate fin heat exchanger characterized in that an inlet and an outlet of a fluid passage to which the header tank is joined are opened only in the header tank.   A heat exchanger main body portion corresponding to the end portion of the header tank having a rounded end portion is a passage in which an inlet and an outlet are not opened in the header tank, and a high-temperature fluid passage and a low-temperature fluid. The plate fin type heat exchanger according to claim 1, wherein a passage different from the passage is disposed.   In the heat exchanger main body portion corresponding to the end portion of the header tank having a rounded end portion, the other fluid passage having no inlet and outlet in the header tank is disposed. The plate fin type heat exchanger according to claim 1, wherein the heat exchanger is a plate fin type heat exchanger. By closing the inlet and outlet of the fluid passage in the heat exchanger main body portion corresponding to the end of the header tank having a rounded end, the inlet and outlet of the fluid passage are placed in the header tank. The plate fin type heat exchanger according to claim 1, wherein the plate fin type heat exchanger is opened only in the plate. The fluid passage in which the inlet and the outlet are closed is closed so that the width of the inlet and the outlet of the fluid passage is narrowed as the end of the end portion of the joint surface of the header tank is approached. Item 5. A plate fin heat exchanger according to Item 4 .

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