JP2009063223A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger capable of dispensing with a header plate and defining a core portion and a header tank. <P>SOLUTION: This heat exchanger comprises a passage unit 2 constituted by fitting U-shaped first and second plates 21, 22 having bottom portions 21a, 22a and a pair of side portions 21b, 22b, in opposition to each other, the bottom portions 21a, 22a of the plates 21, 22 are partially bent to convex an inner face side of the passage unit 2 so that bent portions 21c, 22c are formed, a fin 12 is retained between the bent portions 21c, 22c inside of the passage unit 2, the plurality of passage units 2 are stacked to constitute a core portion 13, a working fluid passage 11 is formed on a position where the bent portions 21c, 22c are opposite to each other between the passage units 2 adjacent to each other, and a tank main body 3 defining a tank internal space with a face orthogonal to the longitudinal direction of the working fluid passage in the passage unit 2, is assembled to both longitudinal ends of the working fluid passage in the core portion 13 to constitute the header tank 14. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a heat exchanger, and in particular, a heat exchanger used in a high temperature / high pressure environment, such as an exhaust heat recovery device that performs heat exchange between exhaust gas discharged from a heat engine and cooling water, The present invention is effective for application to a gas cooler (hereinafter referred to as EGR cooler) for cooling exhaust gas used in an exhaust gas recirculation device (hereinafter referred to as EGR).

  2. Description of the Related Art In recent years, a technology is known in which exhaust heat of exhaust gas is recovered from an exhaust system of a vehicle engine using the principle of a heat pipe, and this exhaust heat is used for promoting warm-up.

In such an exhaust heat recovery device, a heat pipe evaporating part is provided in the exhaust pipe of the engine, and a heat pipe condensing part is provided in the engine cooling water path so that the cooling water is cooled by the exhaust heat of the exhaust gas. Is heated (see, for example, Patent Document 1).
Japanese Patent Laid-Open No. 62-268722

  By the way, a fin-and-tube type heat exchanger is employed as the evaporation part of the exhaust heat recovery unit as described above. That is, the evaporation section includes a plurality of tubes through which the working fluid passes, a core section that is joined to the outer surface of the tubes and has fins that promote heat exchange between the working fluid and the exhaust gas, and both ends of the core section. And a header tank through which working fluid flows in and out. At this time, the plurality of tubes are joined to a header plate that constitutes a tank internal space together with the tank body of the header tank.

  However, in the heat exchanger having such a configuration, the header plate plays a role of partitioning the core portion and the header tank and does not contribute to heat exchange between the exhaust gas and the working fluid. Yes. Further, when assembling the tube, the assembly man-hour for inserting the tube through the header plate is accompanied, and this is a factor that increases the cost of the exhaust heat exchanger as a whole.

  An object of this invention is to provide the heat exchanger which can partition a core part and a header tank without requiring a header plate in view of the said point.

  In order to achieve the above object, in the present invention, bottom surfaces (21a, 22a) having a surface substantially parallel to the flow direction of the second fluid and extending substantially parallel to the longitudinal direction of the first fluid passage (11), A pair of bottom surfaces (21a, 22a) projecting in a direction substantially orthogonal to the bottom surface (21a, 22a) from both longitudinal ends of the first fluid passage (11) and extending substantially parallel to the flow direction of the second fluid. The first and second plates (21, 22) having a substantially U-shaped cross section having the side surfaces (21b, 22b) are fitted to face each other so that the side surfaces (21b, 22b) overlap each other. The passage unit (2) through which the second fluid passes is provided, and a part of the bottom surface portions (21a, 22a) of the first and second plates (21, 22) are part of the passage unit (2). Bent part bent so that the inner surface side is convex ( 1c, 22c), and the bent portions (21c, 22c) are formed over the entire area of the bottom surface (21a, 22a) in the longitudinal direction of the first fluid passage (11), and the fin (12) Is disposed inside the passage unit (2), and is sandwiched between the bent portions (21c, 22c) of the first and second plates (21, 22). The core portion (13) is configured by stacking a plurality of portions of the portions (21a, 22a) excluding the bent portions (21c, 22c) so that the portions are in contact with each other. The first fluid passage (11) is configured at a portion where the portions (21c, 22c) face each other, and a passage unit (2) is provided at both longitudinal ends of the first fluid passage (11) in the core portion (13). ) 1 tank body (3) constituting the tank space together with the longitudinal direction substantially perpendicular to the plane of the fluid path (11) by assembling the is characterized in that the header tank (14) is constructed.

  According to this, since the core part (13) and the header tank (14) can be partitioned by the surface orthogonal to the longitudinal direction of the first fluid passage (11) in the passage unit (2), this heat exchange is performed. In the container, the header plate described in the column of the problem to be solved by the invention can be eliminated. In addition, since the header plate can be eliminated, the number of parts can be reduced, and the assembly man-hour for inserting the first fluid passage (11) into the header plate can be eliminated. Cost can be reduced.

  Moreover, in the heat exchanger of the said characteristic, in the bending part (21g, 22g) between the bottom face part (21a, 22a) and side part (21b, 22b) in a 1st, 2nd plate (21, 22), Even if the angle formed between the surface on the outer side of the passage unit (2) of the bottom surface portion (21a, 22a) and the surface on the outer side of the passage unit (2) of the side surface portion (21b, 22b) is substantially perpendicular. Good.

  According to this, when a plurality of passage units (2) are stacked, it is possible to prevent a gap or groove other than the first fluid passage (11) from being formed between adjacent passage units (2). For this reason, it can prevent that a 1st fluid leaks outside from between a tank main body (3) and a core part (13).

  In the heat exchanger having the above characteristics, the end portion of the side surface portion (22b) of the second plate (22) far from the bottom surface portion (22a) has substantially the same height as the thickness of the first plate (21). A step-down portion (22d) bent inwardly of the passage unit (2), one end side of which is connected to the step-down portion (22d), and is substantially the same as the side surface portion (21b) of the first plate (21). A receiving step portion (22f) having a receiving portion (22e) extending in parallel is provided, and the first plate (21) is fitted so as to be outside the second plate (22). An end portion (210) far from the bottom surface portion (21a) in the side surface portion (21b) of the plate (21) is in contact with the stepped-down portion (22d), and a passage in the side surface portion (21b) of the first plate (21). The inner side of the unit (2) is the receiving part (2 In e), the passage unit (2) is formed so as to be in contact with the outer surface side, and the end portion (210) on the side farthest from the bottom surface portion (21a) in the side surface portion (21b) of the first plate (21) is the bottom surface portion. The taper shape may be inclined in a direction away from the receiving portion (22e) as it is away from (21a).

  According to this, when the first and second plates (21, 22) are fitted together, the side surface portions (21b, 22b) of the plates (21, 22) out of the outer surfaces of the passage unit (2). The surface comprised by each other can be a flat surface. For this reason, it can prevent that a 1st fluid leaks outside from between a tank main body (3) and a core part (13).

  Further, in the heat exchanger having the above characteristics, the bottom surface portion of the side surface portion (21b) of the first plate (21) is formed by fitting the first plate (21) so as to be outside the second plate (22). The end (210) far from (21a) is in contact with the outer surface of another adjacent passage unit (2), and the inner surface side of the passage unit (2) in the side surface (21b) of the first plate (21) is The second plate (22) is formed so as to be in contact with the outer surface side of the passage unit (2) in the side surface portion (22b) and is far from the bottom surface portion (22a) of the side surface portion (21b) of the first plate (21). The side end portion (210) may have a tapered shape that is inclined in a direction away from the side surface portion (22b) of the second plate (22) as the distance from the bottom surface portion (21a) increases.

  According to this, when a plurality of passage units (2) are stacked to form the core portion (13), the side surface portion (21b) of the first plate (21) among the outer surfaces of the core portion (13). ) Can be a flat surface. For this reason, it can prevent that a 1st fluid leaks outside from between a tank main body (3) and a core part (13).

  In the heat exchanger having the above characteristics, the passage unit (2) of the tank body (3) is locked to the core portion (13) at both ends in the stacking direction, and the core portion (13) is connected to the passage unit ( 2) The tank side nail | claw part (33) pressed down from the lamination direction may be provided.

  According to this, when the tank body (3) is locked to the core part (13), the tank side claw part (33) holds the core part (13) from the passage unit (2) stacking direction. Since it plays a role, it is possible to eliminate the need for a dedicated jig at the time of brazing and prepare the work to reduce the manufacturing cost.

  In the heat exchanger having the above characteristics, the heat exchanger includes a cylindrical duct portion (4) having both ends opened, which constitutes a duct through which the second fluid passes, and the first fluid passage (11) in the duct portion (4) is provided. At both ends in the longitudinal direction, there are provided duct side locking portions (41) that lock the core portion (13) from the longitudinal direction of the first fluid passage (11) while locking the core portion (13). May be.

  According to this, when the duct part (4) is locked to the core part (13), the duct side locking part (41) presses the core part (13) from the longitudinal direction of the first fluid passage (11). Since it plays the role of a self jig, a dedicated jig at the time of brazing is not required, and the work can be prepared to reduce the manufacturing cost.

  Further, in the heat exchanger having the above characteristics, on the outer surface side of the passage unit (2) in the bent portions (21c, 22c) of the first and second plates (21, 22), the other adjacent passage unit (2) side Ribs (21h, 22h) are provided so that the ribs (21h, 22h) provided in adjacent passage units (2) are in contact with each other by stacking a plurality of passage units (2). It may be.

  According to this, at the time of brazing, the load applied from the passage unit (2) stacking direction of the core part (13) is transmitted to the passage unit (2) arranged on the inner side of the core part (13). Can do. For this reason, the favorable brazing property between each member is securable.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. In the first embodiment, the heat exchanger according to the present invention is used in an evaporation section of an exhaust heat recovery unit for recovering exhaust heat of exhaust gas from an exhaust system of a vehicle engine and using it as a heat source for an air conditioner or the like. It is applied.

  FIG. 1 is a cross-sectional view showing an exhaust heat recovery device according to the first embodiment. As shown in FIG. 1, the exhaust heat recovery device of the present embodiment includes an evaporation unit 1 and a condensing unit (not shown), and the evaporation unit 1 and the condensing unit are connected to each other to form a loop type. The heat pipe is formed. In the present embodiment, the evaporation unit 1 and the condensing unit are arranged so as to be adjacent in the horizontal direction.

  The heat pipe is provided with a not-shown enclosure, and the inside of the heat pipe is evacuated (depressurized) from the enclosure, and the enclosure is sealed after the working medium is enclosed. Here, water is used as the working medium. As the working medium, alcohol, fluorocarbon, chlorofluorocarbon or the like may be used in addition to water.

  The evaporation unit 1 is disposed in an exhaust cylinder of an engine (not shown). The evaporation unit 1 exchanges heat between the exhaust gas and the working fluid to evaporate the working fluid. The working fluid corresponds to the first fluid of the present invention, and the exhaust gas corresponds to the second fluid of the present invention.

  The condensing part is provided outside the exhaust pipe and is disposed in a cooling water path of an engine (not shown). Further, the condensing unit performs heat exchange between the working fluid evaporated in the evaporating unit 1 and the engine cooling water to condense the working fluid.

  Next, the configuration of the evaporation unit 1 will be described. The evaporation unit 1 includes a core portion 13 having a stacked structure of a working fluid passage 11 through which a working fluid passes and a corrugated fin 12 joined to the outer surface of the working fluid passage 11. A plurality of working fluid passages 11 are arranged in parallel so that the longitudinal direction thereof coincides with the vertical direction. The working fluid passage 11 corresponds to the first fluid passage of the present invention.

  In the evaporation unit 1, header tanks 14 that extend in the stacking direction of the working fluid passages 11 and communicate with all the working fluid passages are provided at both ends in the longitudinal direction of the working fluid passage 11. The header tank 14 is connected to the condensing part through a cylindrical connecting part 15.

  FIG. 2 is an exploded perspective view showing the evaporation section 1 in the first embodiment, and FIG. 3 is an enlarged front view showing a state in which the core section 13 in the first embodiment is viewed from the upstream side of the exhaust gas flow.

  As shown in FIGS. 2 and 3, the core portion 13 of the present embodiment is configured by stacking a plurality of passage units 2 through which exhaust gas passes. The passage unit 2 has a substantially U-shaped cross section, and includes first and second plates 21 and 22 that are fitted so as to face each other.

  More specifically, the first and second plates 21 and 22 have bottom surfaces 21a and 22a having a surface substantially parallel to the exhaust gas flow direction and extending substantially parallel to the longitudinal direction of the working fluid passage, and the bottom surface portion 21a, 22a has a pair of side surface portions 21b and 22b extending from both ends in the longitudinal direction of the working fluid passage in a direction substantially orthogonal to the bottom surface portions 21a and 22a and extending substantially parallel to the exhaust gas flow direction. The passage unit 2 is configured by fitting the first and second plates 21 and 22 so as to face each other so that the side portions 21b and 22b overlap each other.

  Further, the central portions of the bottom surface portions 21a and 22a of the first and second plates 21 and 22 in the exhaust gas flow direction are bent portions 21c and 22c that are bent so that the inner surface side of the passage unit 2 is convex. The bent portions 21c and 22c are continuously formed over the entire area of the bottom surface portions 21a and 22a in the longitudinal direction of the working fluid passage.

  As shown in FIG. 3, the end portion of the side surface portion 22 b of the second plate 22 on the side far from the bottom surface portion 22 a has substantially the same height as the plate thickness of the first plate 21, and is on the inner side of the passage unit 2. A stepped portion 22f having a stepped portion 22d that is bent into one end and a receiving portion 22e that is connected at one end to the stepped portion 22d and extends substantially parallel to the side surface portion 21b of the first plate 21 is formed. And by fitting the 1st plate 21 so that it may become the outside of the 2nd plate 22, while the end part far from the bottom face part 21a in the side part 21b of the 1st plate 21 is in contact with stepped part 22d, A surface on the inner side of the passage unit 2 in the side surface portion 21b of the first plate 21 is in contact with a surface on the outer side of the passage unit 2 in the receiving portion 22e.

  An end portion (hereinafter referred to as a tip portion 210) on the side surface portion 21b of the first plate 21 that is far from the bottom surface portion 21a has a tapered shape that is inclined in a direction away from the receiving portion 22e as the distance from the bottom surface portion 21a increases. For this reason, it is comprised by the side part 21b, 22b of each plate 21 and 22 among the surfaces orthogonal to a working fluid channel | path longitudinal direction among the surfaces of the outer side of the channel | path unit 2, ie, the surface of the channel | path unit 2 outside. The surface that has been formed is a flat surface without a groove or the like.

  In the present embodiment, the surface of the stepped-down portion 22d on the outer side of the passage unit 2 has a tapered shape corresponding to the tip portion 210 of the side surface portion 21b. For this reason, when the 1st, 2nd plates 21 and 22 are fitted together, the step-down part 22e and the front-end | tip part 210 of the side part 21b contact without gap.

  Further, in the bent portions 21g, 22g between the bottom surface portions 21a, 22a and the side surface portions 21b, 22b in the first and second plates 21, 22, the surfaces of the bottom surface portions 21a, 22a on the outer side of the passage unit 2, The angle formed between the side surfaces 21b and 22b and the outer surface of the passage unit 2 is substantially a right angle. That is, the bent portions 21g and 22g between the bottom surface portions 21a and 22a and the side surface portions 21b and 22b in the first and second plates 21 and 22 are minimum R.

  The corrugated fin 12 is disposed inside each passage unit 2 and is sandwiched between the bent portions 21 c and 22 c of the first and second plates 21 and 22. That is, the corrugated fins 12 are held between the bent portions 21 c and 22 c of the plates 21 and 22.

  And as shown in FIG.1 and FIG.2, by laminating | stacking the above-mentioned channel | path unit 2 two or more so that the site | parts except the bending parts 21c and 22c in the bottom face parts 21a and 22a of each plate 21 and 22 may contact. The core unit 13 is configured. At this time, the working fluid passage 11 is configured in a portion where the bent portions 21c and 22c between the adjacent passage units 2 face each other. In the present embodiment, the bent portions 21c and 22c are provided with ribs 21h and 22h protruding outward from the passage unit 2, and when a plurality of passage units 2 are stacked, the adjacent passage units 2 are adjacent to each other. The ribs 21g and 22g are in contact with each other.

  In addition, in both ends of the core fluid 13 in the longitudinal direction of the working fluid passage, spaces in the tank together with surfaces orthogonal to the longitudinal direction of the working fluid passage in the core portion 13, that is, side surfaces 21 b and 22 b of the first and second plates 21 and 22. The tank main body 3 which comprises is assembled | attached, and the header tank 14 is comprised by this. The tank body 3 has a three-dimensional shape in which the inside is a space and one side is open, and the space forming part 31 is configured so that the inside and all the working fluid passages 11 communicate with each other through the opening. And a flange portion 32 formed at the peripheral edge portion of the opening portion 31. The space forming part 31 is formed with a through hole 31 a to which the communication part 15 is connected. The flange portion 32 comes into contact with a surface perpendicular to the longitudinal direction of the working fluid passage of the core portion 13, that is, the side surface portions 21 b and 22 b of the first and second plates 21 and 22 without a gap. In the present embodiment, the flange portion 32 extends in the exhaust gas flow direction so that the end portion in the exhaust gas flow direction corresponds to the end portion in the exhaust gas flow direction of the core portion 13.

  Tank side claw portions 33 for locking the tank body 3 to the core portion 13 are provided at both ends of the flange portion 32 in the passage unit stacking direction. The tank side claw portion 33 serves as a self jig for pressing the core portion 13 from the passage unit stacking direction when the tank body 3 is assembled to the core portion 13.

Moreover, as shown in FIG. 2, the cylindrical duct part 4 which the both ends open which comprises the duct which exhaust gas passes is assembled | attached to the both ends of the exhaust gas flow direction in the core part 13. As shown in FIG. The duct portion 4 is provided with a duct side locking portion 41 that protrudes toward the core portion 13 and locks the duct portion 4 to the core portion 13.
The duct side locking portion 41 serves as a self jig for pressing the core portion 13 and the flange portion 32 of the tank body 3 from the longitudinal direction of the working fluid passage when the duct portion 4 is assembled to the core portion 13. In the present embodiment, the duct side locking portion 41 is configured as a cylindrical member having a diameter larger than that of the duct portion 4 and is integrally formed with the duct portion 4. And when the duct part 4 is assembled | attached to the core part 13, the duct side latching | locking part 41 presses the flange part 32 of the tank main body 3 over the whole channel unit lamination direction.

  Next, the manufacturing method of the evaporation part 1 of the exhaust heat recovery device according to the first embodiment will be described.

  First, in a state where the corrugated fins 12 are sandwiched between the first and second plates 21 and 22, the plates 21 and 22 are overlapped so as to face each other so that the first plate 21 is outside the second plate 22. The passage unit 2 is formed by And the core part 13 is formed by laminating | stacking predetermined number of this channel | path unit 2 so that the bottom face parts 21a and 22a of each plate 21 and 22 may contact.

  And the tank main body 3 is assembled | attached to the working fluid passage longitudinal direction both ends of the core part 13. FIG. Specifically, the tank body 3 is fixed to the core portion 13 by locking the tank side claw portions 33 of the tank body 3 to both ends of the core portion 13 in the passage unit stacking direction. Subsequently, the duct portion 4 is assembled to both ends of the core portion 13 in the exhaust gas flow direction. Specifically, the duct portion 4 is fixed to the core portion 13 by locking the duct side locking portion 41 of the duct portion 4 to the flange portion 32 of the tank body 3 assembled to the core portion 13.

  As described above, all the components of the evaporation unit 1 are assembled together. Then, with all the components assembled, a jig (not shown) is applied from both sides of the core portion 13, that is, from both sides in the passage unit stacking direction, and a predetermined load is applied in the passage unit stacking direction. In this way, all the components are temporarily fixed, and the components are put into the heating furnace in this state, and all the components are brazed together. At this time, the working fluid passage 11 is formed between the adjacent passage units 2 by joining the plurality of passage units 2 in contact with each other. In this embodiment, all the components of the evaporation unit 1 are made of stainless steel, and a nickel alloy is used as a brazing material during brazing.

  As described above, the passage unit 2 is formed by fitting the first and second plates 21 and 22 having a substantially U-shaped cross section to face each other, and a plurality of the passage units 2 are stacked to form the core portion 13. The header tank 14 is configured by assembling the tank body 3 that constitutes the tank inner space together with the side surface portions 21b and 22b of the first and second plates 21 and 22 to the core portion 13, The core portion 13 and the header tank 14 can be partitioned by the side portions 21 b and 22 b of the second plates 21 and 22. For this reason, in the exhaust heat recovery device of the present embodiment, the header plate described in the column of the problem to be solved by the invention can be eliminated. Further, since the header plate can be eliminated, the number of parts can be reduced, and the assembly man-hour for inserting the working fluid passage 11 through the header plate can be eliminated, thereby reducing the cost as an exhaust heat recovery device. Can be reduced.

  By the way, in the heat exchanger described in the column of the problem to be solved by the above invention, side plates for reinforcing the core portion may be provided at both ends of the core portion in the tube stacking direction. This side plate is joined to the header plate and serves as a self jig for pressing the fin from the tube stacking direction. On the other hand, in the present embodiment, the corrugated fins 12 are arranged inside the respective passage units 2 and are held and fixed between the bent portions 21c and 22c of the first and second plates 21 and 22, so that the side plate Can be abolished.

  Further, the tip portion 210 of the side surface portion 21b of the first plate 21 is tapered so as to be away from the receiving portion 22e as it is away from the bottom surface portion 21a, and the tip portion 210 is brought into contact with the step-down portion 22d. Thus, when the first and second plates 21 and 22 are fitted together, of the outer side surfaces of the passage unit 2, the surfaces formed by the side portions 21b and 22b of the plates 21 and 22, that is, the respective passages The outer surface of the surface orthogonal to the longitudinal direction of the working fluid passage of the unit 2 can be a flat surface. Thereby, since the flange part 32 of the tank main body 3 and the surface orthogonal to the working fluid passage longitudinal direction of the core part 13 can be closely_contact | adhered, a working fluid leaks outside between the tank main body 3 and the core part 13. Can be prevented.

  Similarly, in the bent portions 21g and 22g between the bottom surface portions 21a and 22a and the side surface portions 21b and 22b in the first and second plates 21 and 22, the surfaces of the bottom surface portions 21a and 22a on the outer side of the passage unit, By making the angle formed between the side surfaces 21b and 22b and the surface on the outer side of the passage unit at a right angle, when a plurality of passage units 2 are stacked, gaps other than the working fluid passage 11 between adjacent passage units 2 A groove can be prevented from being formed. That is, the outer surface of the surface orthogonal to the working fluid passage longitudinal direction of the core portion 13 can be a flat surface. Thereby, since the flange part 32 of the tank main body 3 and the surface orthogonal to the working fluid passage longitudinal direction of the core part 13 can be closely_contact | adhered, a working fluid leaks outside between the tank main body 3 and the core part 13. Can be prevented.

  In addition, the tank main body 3 is provided with a tank side claw portion 33 that engages the core portion 13 at both ends of the tank main body 3 in the passage unit stacking direction and holds the core portion 13 from the passage unit stacking direction. Since the tank side claw 33 plays the role of a self jig that holds the core 13 from the passage unit stacking direction when it is locked to the section 13, a dedicated jig for brazing is not required and the work is performed. Preparation costs can be reduced.

  Further, the duct portion 4 is provided with a duct side locking portion 41 that is locked to the core portion 13 at both ends in the longitudinal direction of the working fluid passage of the duct portion 4 and holds the core portion 13 from the longitudinal direction of the working fluid passage. When 4 is locked to the core portion 13, the duct side locking portion 41 serves as a self jig that presses the core portion 13 from the longitudinal direction of the working fluid passage, thus eliminating the need for a dedicated jig for brazing. At the same time, the cost can be reduced by preparing the work.

  In addition, ribs 21h and 22h projecting toward the other adjacent passage unit 2 are provided on the outer surface side of the passage unit 2 in the bent portions 21c and 22c of the first and second plates 21 and 22, and a plurality of the passage units 2 are stacked. In this case, the ribs 21h and 22h provided in the adjacent passage unit 2 are in contact with each other, so that the load applied from the passage unit stacking direction of the core portion 13 during brazing It can transmit to the channel | path unit 2 arrange | positioned at the side. For this reason, the favorable brazing property between each member is securable.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. The same parts as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted. FIG. 4 is an enlarged front view showing a state in which the core portion 13 in the second embodiment is viewed from the exhaust gas flow upstream side.

  As shown in FIG. 4, the length of the bottom surface portion 22 a of the second plate 22 in the longitudinal direction of the working fluid passage is longer than the length of the bottom surface portion 21 a of the first plate 21 in the longitudinal direction of the working fluid passage. It is shortened by twice the thickness. For this reason, when the first plate 21 is fitted so as to be outside the second plate 22, the inner surface side of the side surface portion 21b of the first plate 21 and the outer surface side of the side surface portion 22b of the second plate 22 are It comes to contact.

  Further, the first plate 21 is formed such that the front end portion 210 of the side surface portion 21 b comes into contact with the bent portion 21 g of the other first plate 21 constituting the adjacent passage unit 2. Moreover, the front-end | tip part 210 of the 1st plate 21 becomes the taper shape which inclined in the direction which leaves | separates from the side part 22b of the 2nd plate 22 as it leaves | separates from the bottom face part 21a.

  According to the second embodiment, when the core portion 13 is formed by stacking a plurality of passage units 2, the side portion 21 b of the first plate 21 is formed on the outer side surface of the core portion 13. The surface can be a flat surface. Thereby, since the flange part 32 of the tank main body 3 and the surface orthogonal to the working fluid passage longitudinal direction of the core part 13 can be closely_contact | adhered, a working fluid leaks outside between the tank main body 3 and the core part 13. Can be prevented.

(Other embodiments)
In each of the above embodiments, the example in which the heat exchanger according to the present invention is applied to the exhaust heat recovery device has been described. May be.

  In the first embodiment, the duct side locking portion 41 is described as an example of a cylindrical member having a diameter larger than that of the duct portion 4. You may comprise as a nail-like member to stop.

  Moreover, although the said 1st Embodiment demonstrated the example which made the taper shape corresponding to the front-end | tip part 210 of the side part 21b in the channel unit 2 outer side surface of the step-down part 22d, it does not restrict to this. The step-down portion 22d can have any shape.

  In the first embodiment, the tip portion 210 of the side surface portion 21b of the first plate 21 has been described as an example having a tapered shape that is inclined in a direction away from the receiving portion 22e as it is away from the bottom surface portion 21a. An angle formed between the surface of the side surface portion 22b on the outer side of the passage unit 2 and the surface of the stepped portion 22d on the outer side of the passage unit 2 at the bent portion between the side surface portion 22b and the step-down portion 22d. Is formed so as to have a substantially right angle, the tip portion 210 of the first plate 21 may not be tapered. Even in this case, the outer surface of the surface orthogonal to the longitudinal direction of the working fluid passage of each passage unit 2 can be a flat surface.

  In the second embodiment, an example is described in which the tip portion 210 of the side surface portion 21b of the first plate 21 is tapered so as to be inclined away from the side surface portion 22b of the second plate 22 as the distance from the bottom surface portion 21a increases. However, in the bent portion 21g, the angle formed between the surface of the bottom surface portion 21a on the outer side of the passage unit 2 and the surface of the side surface portion 21b on the outer side of the passage unit 2 is substantially perpendicular. When formed, the tip portion 210 of the first plate 21 does not have to be tapered. Even in this case, the outer surface of the surface perpendicular to the longitudinal direction of the working fluid passage of the core portion 13 can be a flat surface.

It is sectional drawing which shows the exhaust heat recovery device which concerns on 1st Embodiment. It is a disassembled perspective view which shows the evaporation part 1 in 1st Embodiment. It is an enlarged front view which shows the state which looked at the core part 13 in 1st Embodiment from the exhaust gas flow upstream. It is an enlarged front view which shows the state which looked at the core part 13 in 2nd Embodiment from the exhaust gas flow upstream.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 2 ... Passage unit, 3 ... Tank main body, 4 ... Duct part, 11 ... Working fluid passage (1st fluid passage), 12 ... Corrugated fin, 13 ... Core part, 14 ... Header tank, 21 ... 1st plate, 22 ... 2nd plate, 21a, 22a ... bottom surface portion, 21b, 22b ... side surface portion, 21c, 22c ... bent portion, 21g, 22g ... bent portion, 21h, 22h ... rib, 22d ... step-down portion, 22e ... receiving portion, 22f ... Step receiving part, 33 ... Tank side claw part, 41 ... Duct side locking part.

Claims (7)

A plurality of first fluid passages (11) through which the first fluid passes, and a second fluid joined to the outer periphery of the first fluid passage (11) and flowing around the first fluid and the first fluid passage (11). A core portion (13) having a laminated structure with fins (12) for promoting heat exchange with a fluid;
A header that is located on the longitudinal end side of the first fluid passage (11), extends in a direction orthogonal to the longitudinal direction of the first fluid passage (11), and communicates with the plurality of first fluid passages (11). A heat exchanger comprising a tank (14),
A bottom surface (21a, 22a) having a surface substantially parallel to the flow direction of the second fluid and extending substantially parallel to the longitudinal direction of the first fluid passage (11); and the bottom surface (21a, 22a) A pair of side surface portions (21b) projecting in a direction substantially orthogonal to the bottom surface portions (21a, 22a) from both longitudinal ends of the first fluid passage (11) and extending substantially parallel to the flow direction of the second fluid. 22b), and the first and second plates (21, 22) having a substantially U-shaped cross section are fitted to each other so that the side surface portions (21b, 22b) overlap each other, A passage unit (2) through which the second fluid passes,
Part of the bottom surface portions (21a, 22a) of the first and second plates (21, 22) are bent portions (21c, 22c) bent so that the inner surface side of the passage unit (2) is convex. And
The bent portions (21c, 22c) are formed over the entire area in the longitudinal direction of the first fluid passage (11) in the bottom surface portions (21a, 22a),
The fin (12) is disposed inside the passage unit (2) and is sandwiched between the bent portions (21c, 22c) of the first and second plates (21, 22).
The core unit (13) is configured by stacking a plurality of the passage units (2) such that portions of the bottom surface portions (21a, 22a) except the bent portions (21c, 22c) are in contact with each other. And
The first fluid passage (11) is configured at a portion where the bent portions (21c, 22c) face each other between the adjacent passage units (2).
A space in the tank is formed at both ends in the longitudinal direction of the first fluid passage (11) in the core portion (13) together with surfaces substantially perpendicular to the longitudinal direction of the first fluid passage (11) in the passage unit (2). The heat exchanger according to claim 1, wherein the header tank (14) is configured by assembling the tank body (3). In the bent portions (21g, 22g) between the bottom surface portions (21a, 22a) and the side surface portions (21b, 22b) of the first and second plates (21, 22), the bottom surface portions (21a, 22a) The angle formed between the outer surface of the passage unit (2) and the outer surface of the passage unit (2) of the side surface portions (21b, 22b) is substantially perpendicular. The heat exchanger according to claim 1. An end portion of the side surface portion (22b) of the second plate (22) on the side far from the bottom surface portion (22a) has substantially the same height as the thickness of the first plate (21), and the passage A step-down portion (22d) bent inward of the unit (2) and one end side thereof are connected to the step-down portion (22d), and substantially parallel to the side surface portion (21b) of the first plate (21). A receiving step portion (22f) having an extending receiving portion (22e) is provided;
When the first plate (21) is fitted so as to be outside the second plate (22), it is far from the bottom surface portion (21a) in the side surface portion (21b) of the first plate (21). The side end portion (210) is in contact with the step-down portion (22d), and the inner surface side of the passage unit (2) in the side surface portion (21b) of the first plate (21) is in the receiving portion (22e). The passage unit (2) is formed so as to be in contact with the outer surface side,
A direction in which the end (210) of the side surface (21b) of the first plate (21) on the side farther from the bottom surface (21a) moves away from the receiving portion (22e) as the distance from the bottom surface (21a) increases. The heat exchanger according to claim 1, wherein the heat exchanger has a tapered shape inclined to the top. When the first plate (21) is fitted so as to be outside the second plate (22), it is far from the bottom surface portion (21a) in the side surface portion (21b) of the first plate (21). The side end portion (210) is in contact with the outer surface side of the other adjacent passage unit (2), and the inner surface side of the passage unit (2) in the side surface portion (21b) of the first plate (21) is The second plate (22) is formed so as to be in contact with the outer surface side of the passage unit (2) in the side surface portion (22b),
An end portion (210) of the side surface portion (21b) of the first plate (21) that is farther from the bottom surface portion (22a) is separated from the bottom surface portion (21a) as the second plate (22) has the end portion (210). The heat exchanger according to any one of claims 1 to 3, wherein the heat exchanger has a tapered shape inclined in a direction away from the side surface (22b). The tank body (3) is locked to the core portion (13) at both ends of the passage unit (2) in the stacking direction, and the core portion (13) is connected to the passage unit (2) from the stacking direction. The heat exchanger according to any one of claims 1 to 4, further comprising a tank side claw portion (33) for pressing. A cylindrical duct part (4) having both ends opened, which constitutes a duct through which the second fluid passes,
The longitudinal direction both ends of the first fluid passage (11) in the duct portion (4) are locked to the core portion (13), and the core portion (13) is connected to the first fluid passage ( The heat exchanger according to any one of claims 1 to 5, further comprising a duct side latching portion (41) for pressing from the longitudinal direction of 11). On the outer surface side of the passage unit (2) in the bent portions (21c, 22c) of the first and second plates (21, 22), ribs (21h) protruding toward the other adjacent passage unit (2) side 22h),
The ribs (21h, 22h) provided in the adjacent passage units (2) are in contact with each other by stacking a plurality of the passage units (2). The heat exchanger according to any one of 6.

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