JP2018091500A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To inhibit effects on a seal member caused by deformation of an accommodation section even when thermal expansion coefficients of a case and a heat exchange section differ from each other.SOLUTION: A heat exchanger 100 for exchanging heat between EGR gas and engine cooling water includes: a heat exchange section 1 in which the EGR gas flows; a case 30 in which the heat exchange section 1 is accommodated and the engine cooling water flows; a seal accommodation section 18 defined by an outer peripheral surface 17e of a header member 17 of the heat exchange section 1 formed in a flowing direction of the EGR gas, an inner peripheral surface 31e of a case body 31 of the case 30 opposing to the outer peripheral surface 17e of the header member 17, and an end surface 31f erected from the inner peripheral surface 31e of the case body 31; and an O-ring 17c accommodated in the seal accommodation section 18 to separate a flow passage of the EGR gas and a flow passage of the engine cooling water from each other.SELECTED DRAWING: Figure 6

Description

  The present invention relates to a heat exchanger.

  Patent Document 1 discloses an EGR (Exhaust Gas Recirculation) gas cooling device in which a heat exchanging portion formed by supporting both ends of a plurality of pipes with end plates is accommodated in an EGR pipe. In this EGR gas cooling device, the outer cylinder that accommodates the heat exchange part is formed of resin.

Japanese Patent Laid-Open No. 11-013554

  By the way, when the metal heat exchange part is housed in the resin outer cylinder, the seal member housed in the housing part between them is affected by the deformation of the housing part due to the difference in thermal expansion coefficient between them. There is a risk of receiving.

  The present invention has been made in view of the above problems, and suppresses the influence on the sealing material due to the deformation of the housing portion even when the case and the heat exchange portion have different coefficients of thermal expansion. With the goal.

  According to an aspect of the present invention, a heat exchanger that performs heat exchange between a first fluid and a second fluid includes a heat exchange portion through which the first fluid flows and the heat exchange portion. A case in which the second fluid circulates, an outer peripheral surface of the heat exchange portion formed along the flow direction of the first fluid, and an inner peripheral surface of the case facing the outer peripheral surface of the heat exchange portion A seal accommodating portion defined by an end surface formed upright from an inner peripheral surface of the case or an outer peripheral surface of the heat exchange portion, and a flow of the first fluid accommodated in the seal accommodating portion. And a sealing material that separates the path and the second fluid flow path.

  In the said aspect, a seal | sticker accommodating part is formed with the outer peripheral surface of a heat exchange part, the inner peripheral surface of a case, and the end surface of a case or a heat exchange part. Therefore, even if the case and the heat exchange coefficient are different from each other, only the inner peripheral surface of the case and the outer peripheral surface of the heat exchange part slide relatively, the shape of the seal housing part is does not change. Therefore, a shearing force does not act on the sealing material accommodated in the seal accommodating portion. Therefore, the influence on the sealing material due to the deformation of the seal housing portion can be suppressed.

FIG. 1 is an exploded perspective view of a heat exchanger according to the first embodiment of the present invention. FIG. 2 is a perspective view of the heat exchanger according to the first embodiment of the present invention. FIG. 3 is a perspective view showing a state in which the case of the heat exchanger according to the first embodiment of the present invention is removed. FIG. 4 is a plan sectional view of the heat exchanger according to the first embodiment of the present invention. FIG. 5 is a side sectional view of the heat exchanger according to the first embodiment of the present invention. FIG. 6 is an enlarged view of the periphery of the sealing material in FIG. FIG. 7 is an enlarged view of the periphery of the sealing material in the heat exchanger according to the modification of the first embodiment of the present invention. FIG. 8 is an enlarged view of the periphery of a sealing material in a heat exchanger according to another modification of the first embodiment of the present invention. FIG. 9 is a plan sectional view of a heat exchanger according to the second embodiment of the present invention. FIG. 10 is a plan sectional view of a heat exchanger according to the third embodiment of the present invention.

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

(First embodiment)
First, with reference to FIGS. 1 to 8, a heat exchanger 100 according to a first embodiment of the present invention will be described.

  The heat exchanger 100 is provided in an EGR device that recirculates a part of exhaust gas combusted in a combustion chamber of an engine (not shown) to the combustion chamber as EGR (Exhaust Gas Recirculation) gas. The heat exchanger 100 is an EGR cooler that performs heat exchange between the EGR gas (first fluid) and the engine coolant (second fluid) that cools the engine to cool the EGR gas.

  The heat exchanger 100 includes a laminated core 10 that exchanges heat between EGR gas and engine coolant, a clip 20 as a restraining member that restrains the laminated core 10 in the laminating direction, and an inner side in which the laminated core 10 is accommodated. And a case 30 through which engine coolant flows.

  The laminated core 10 includes a plurality of tubes 11 to be laminated, inner fins 12 accommodated in the tubes 11, and a plate 13 to which the laminated tubes 11 are attached. The laminated core 10 is formed such that a plurality of tubes 11 are laminated to form a rectangular parallelepiped shape. The laminated core 10 is formed of a metal material such as stainless steel. In each tube 11, a flow path through which EGR gas flows is formed, and a flow path through which engine cooling water flows is formed between the plurality of tubes 11.

  A header member 16 that guides the EGR gas supplied from the supply pipe 41 (see FIG. 3) to each tube 11 is provided at the EGR gas inlet in the laminated core 10. At the outlet of the EGR gas in the laminated core 10, a header member 17 that collects the EGR gas discharged from each tube 11 and guides it to the discharge pipe 42 is provided. In the heat exchanger 100, the laminated core 10 and the header member 17 constitute the heat exchange unit 1.

  The tube 11 has a tube inner 11a and a tube outer 11b provided to face each other. Both the tube inner 11a and the tube outer 11b are formed in a flat plate shape having a concave cross section. The tube inner 11a and the tube outer 11b are assembled so that the recesses face each other and the tube outer 11b covers the outside of the tube inner 11a. The tube inner 11a and the tube outer 11b form a space in which the inner fins 12 are accommodated.

  In the tube outer 11b, a plurality of protrusions 11c that abut on another tube 11 adjacent in a stacked state and have a predetermined interval with the other tube 11, and a flow path through which engine coolant flows. A pair of bulging portions 11d to be partitioned is formed.

  The protrusion 11 c is formed to protrude in the stacking direction of the tubes 11. The protrusion 11c is formed at a position where the bulging portion 11d of the tube 11 is not provided. Between the pair of adjacent tubes 11, a flow path through which the engine coolant flows is formed by the height of the protrusion 11c.

  The bulging portions 11d are formed at both ends of the tube 11 in the EGR gas flow direction. The bulging portion 11 d protrudes in the same direction as the projection 11 c in the stacking direction of the tubes 11. 11 d of bulging parts contact | abut with the other adjacent tube 11 in the laminated | stacked state, and are united by brazing. Thereby, the flow path of the engine cooling water between the pair of adjacent tubes 11 is closed with respect to the flow path of the EGR gas.

  The inner fins 12 are accommodated in a space formed between the tube inner 11a and the tube outer 11b. The inner fins 12 are offset fins in which adjacent irregularities are offset from each other. The inner fin 12 agitates the flow of EGR gas in the tube 11. Further, the provision of the inner fins 12 increases the surface area for the EGR gas to exchange heat. Therefore, the heat exchange efficiency can be improved by providing the inner fins 12.

  Note that an outer fin may be provided between a pair of adjacent tubes 11 without providing the inner fin 12. In this case, it is not necessary to form the protrusion 11c on the tube 11.

  In order to fix the laminated core 10 to the case 30, the plate 13 is formed in a rectangular frame shape. The laminated core 10 is fixed to the inner periphery of the plate 13 via the header member 16. The plate 13 has a plurality of crimping claws 13 a for fixing the case 30 on the side where the laminated core 10 is provided.

  At one end of the header member 16, a rectangular portion 16a formed in a rectangular shape is provided. The rectangular portion 16 a is inserted into the inner periphery of the plate 13. The laminated core 10 is inserted into the inner periphery of the rectangular portion 16a. The rectangular portion 16 a is formed so as to cover the bulging portion 11 d in the tube 11 from the end portion of the tube 11. The other end of the header member 16 is provided with a cylindrical portion 16b formed in a cylindrical shape. The cylindrical portion 16 b is connected to the supply pipe 41. The header member 16 is formed such that the cylindrical portion 16b is the smallest and the rectangular portion 16a is the largest.

  The header member 16 is brazed and integrated with the laminated core 10 and the plate 13. Similar to the tube 11, the header member 16 is formed of a metal material such as stainless steel, for example.

  The header member 17 is inserted into the inner periphery of the case 30. One end of the header member 17 is provided with a rectangular portion 17a formed in a rectangular shape. The laminated core 10 is inserted into the inner periphery of the rectangular portion 17a. The rectangular portion 17 a is formed so as to cover the bulging portion 11 d in the tube 11 from the end portion of the tube 11. The header member 17 covers the lower ends of the plurality of tubes 11 in the EGR gas flow direction. The other end of the header member 17 is provided with a cylindrical portion 17b formed in a cylindrical shape. The header member 17 is formed such that the cylindrical portion 17b is the smallest and the rectangular portion 17a is the largest.

  As with the header member 16, the header member 17 is brazed and integrated with the laminated core 10. Similarly to the tube 11, the header member 17 is also made of a metal material such as stainless steel.

  As shown in FIGS. 4 and 5, the cylindrical portion 17 b includes an O-ring 17 c as a sealing material housed in the seal housing portion 18, and a backup ring 17 d as a ring member for fixing the O-ring 17 c in the case 30. , Is held on the inner periphery of the case 30. Thereby, it is possible to prevent the engine coolant flowing through the case 30 from leaking into the EGR gas flow path. The cylindrical portion 17 b is connected to the discharge pipe 42 through the case 30. The O-ring 17c and the seal accommodating portion 18 in which the O-ring 17c is accommodated will be described in detail later with reference to FIGS.

  As shown in FIG. 1, the clip 20 is formed in a U shape so as to come into contact with three of the four side surfaces of the rectangular parallelepiped laminated core 10. As shown in FIG. 3, the clip 20 is fitted between the protrusions 11 c of the tube 11. Thereby, the clip 20 engages with the protrusion 11c, and the movement with respect to the tube 11 is restricted. The clip 20 supports the laminated core 10 in the lamination direction with respect to the case 30. The clip 20 has a leaf spring portion 21 as an elastic support portion that elastically supports the laminated core 10 in the lamination direction with respect to the case 30.

  The clip 20 forms the laminated core 10 by restraining the plurality of tubes 11 before brazing from the outer periphery in the laminating direction. The clip 20 is brazed to the laminated core 10 in a state where the laminated core 10 is constrained, and is integrated with the laminated core 10. Similar to the tube 11, the clip 20 is formed of a metal material such as stainless steel.

  The clip 20 may be attached to the laminated core 10 by being provided as a separate member from the laminated core 10 instead of being brazed to the laminated core 10. In this case, the clip 20 may be formed of a spring steel material or a heat resistant resin material.

  The leaf spring portions 21 are provided at both ends of the laminated core 10 in the lamination direction. The leaf spring portion 21 is deformed when the laminated core 10 is thermally expanded by the high-temperature EGR gas flowing through the inner periphery of the tube 11 and absorbs the change in the outer shape of the laminated core 10. The leaf spring portion 21 is formed so as to protrude outward from the laminated core 10 toward the rear in the insertion direction of the clip 20 into the case 30. Thereby, when the laminated core 10 is inserted into the case 30, the leaf spring portion 21 of the clip 20 is prevented from being caught in the case 30, and the laminated core 10 can be easily inserted into the case 30.

  The case 30 includes a case main body 31 that houses the laminated core 10, a supply flow path 32 for supplying engine cooling water, and a discharge flow path 33 for discharging engine cooling water.

  The case body 31 is formed in a cylindrical shape so as to cover the laminated core 10 inserted from the opening 31a. As shown in FIG. 2, the case main body 31 is fixed to the plate 13 by bending the crimping claws 13 a. As shown in FIGS. 3 to 5, an O-ring 13 b is provided between the opening 31 a of the case body 31 and the plate 13. The O-ring 13b is crushed between the case body 31 and the plate 13 when the crimping claw 13a is bent. Thereby, it is possible to prevent the engine coolant flowing through the case 30 from leaking into the EGR gas flow path.

  The case body 31 includes a cooling water supply port 31b to which engine cooling water for cooling the EGR gas flowing through the tube 11 of the laminated core 10 is supplied, and cooling water from which the engine cooling water that has cooled the EGR gas is discharged. A discharge port 31c.

  A discharge pipe 42 is attached to an end 31 d of the case body 31 opposite to the opening 31 a via an O-ring 42 a and a backup ring 42 b that fixes the O-ring 42 a to the case 30. The discharge pipe 42 is fixed to the case 30 by a spring 42c formed in a U shape. The case main body 31 has a reduced diameter portion 31g formed in a funnel shape so that the diameter is gradually reduced from the portion accommodating the laminated core 10 and the header member 17 toward the end portion 31d.

  The supply flow path 32 is attached to the side surface of the case main body 31. The supply flow path 32 guides cooling water supplied from the cooling water supply port 31 b of the case main body 31 into the case main body 31. As shown in FIG. 5, the cooling water supplied from the cooling water supply port 31 b is supplied into the case main body 31 after being led to the vicinity of one end of the laminated core 10.

  The discharge channel 33 is attached to the same side as the supply channel 32 of the case body 31 is attached. The discharge flow path 33 guides the cooling water discharged from the cooling water discharge port 31 c of the case body 31. As shown in FIG. 5, the engine coolant that has cooled the EGR gas is led to the vicinity of the other end of the laminated core 10 and then discharged from the case body 31 to the outside.

  Next, the O-ring 17c and the seal housing portion 18 in which the O-ring 17c is housed will be described with reference to FIGS.

  As shown in FIG. 6, the seal accommodating portion 18 includes an outer peripheral surface 17e of the header member 17 formed along the EGR gas flow direction, an inner peripheral surface 31e of the case body 31 facing the outer peripheral surface 17e, An end surface 31f formed upright from the inner peripheral surface 31e of the main body 31 is annularly defined. The end surface 31 f is a stepped portion formed by reducing the diameter of the case body 31 and standing from the inner peripheral surface 31 e toward the outer peripheral surface 17 e of the header member 17.

  The outer peripheral surface 17e is a flat surface or a smooth surface formed of a metal material such as stainless steel. The O-ring 17c and the backup ring 17d are disposed between the inner peripheral surface 31e and the outer peripheral surface 17e of the case body 31.

  The outer peripheral surface 17e may be a smooth surface that has been subjected to surface lubricity treatment and has improved slidability.

  The O-ring 17 c is formed in an annular shape corresponding to the shape of the seal housing portion 18. The O-ring 17 c is crushed between the outer peripheral surface 17 e of the header member 17 and the inner peripheral surface 31 e of the case main body 31. Thus, the O-ring 17c seals to isolate the EGR gas flow path from the engine coolant flow path.

  The backup ring 17 d is press-fitted into the inner peripheral surface 31 e of the case body 31 and is fixed to the case body 31. The backup ring 17d does not contact the outer peripheral surface 17e of the header member 17, and is provided with a minute gap between the backup ring 17d and the outer peripheral surface 17e. The backup ring 17d forms a space in which the O-ring 17c is accommodated between the end surface 31f of the case body 31. The seal housing portion 18 is closed by the backup ring 17d. Thereby, the position of the O-ring 17c is defined.

  Thus, the seal housing portion 18 is formed by the outer peripheral surface 17e of the header member 17, the inner peripheral surface 31e of the case main body 31, and the end surface 31f of the case main body 31. Therefore, even if the case 30 and the heat exchange part 1 have different coefficients of thermal expansion, the inner peripheral surface 31e of the case body 31 and the outer peripheral surface 17e of the header member 17 in the heat exchange part 1 slide relatively. The shape of the seal accommodating portion 18 is not changed. Therefore, the shearing force does not act on the O-ring 17c accommodated in the seal accommodating portion 18. Therefore, the influence on the O-ring 17c due to the deformation of the seal housing portion 18 can be suppressed.

  As shown in FIG. 6, a gap is formed between the end portion 17 f of the header member 17 and the inner surface of the reduced diameter portion 31 g of the case main body 31.

  Usually, in the heat exchange part 1 made of a metal member and the case 30 made of a resin member, the case 30 has a higher coefficient of thermal expansion than the heat exchange part 1. Therefore, when the temperature rises to the same temperature, the case 30 that is a resin member has a larger amount of thermal expansion than the heat exchange unit 30.

  On the other hand, in the heat exchanger 100, the high temperature EGR gas flows through the heat exchanging unit 1 and becomes high temperature. However, since the cooling water circulates inside the case 30, the inside of the case 30 is not so hot. Therefore, the heat exchanging portion 1 made of a metal member is thermally expanded more than the case 30. Therefore, a gap is formed so that the heat exchanging portion 1 can be more thermally expanded than the case 30.

  This gap corresponds to the “range that can be moved by thermal expansion” shown in FIG. The gap is formed larger than the difference in thermal expansion between the case 30 and the heat exchange unit 1 when the heat exchange unit 1 rises to the maximum temperature. Therefore, the end portion 17f of the header member 17 and the inner surface of the reduced diameter portion 31g of the case body 31 do not hit each other.

  In addition, you may seal directly between the laminated core 10 and the case 30 without providing the header member 17 like the modification shown in FIG. In this case, the seal housing portion 18 includes an outer peripheral surface 10a of the laminated core 10 formed along the EGR gas flow direction, an inner peripheral surface 31e of the case main body 31 facing the outer peripheral surface 10a, and an inner portion of the case main body 31. An end surface 31f formed upright from the peripheral surface 31e is annularly defined.

  The outer peripheral surface 10a is a flat surface (flat surface) or a smooth surface formed of a metal material such as stainless steel. The O-ring 17c and the backup ring 17d are disposed between the inner peripheral surface 31e and the outer peripheral surface 10a of the case body 31.

  The outer peripheral surface 10a may be a smooth surface that has been subjected to surface lubricity treatment to improve the slipperiness.

  As described above, when the seal housing portion 18 is formed by the outer peripheral surface 10 a of the laminated core 10, the inner peripheral surface 31 e of the case body 31, and the end surface 31 f of the case body 31, the seal housing portion 18 is similarly housed in the seal housing portion 18. The shearing force does not act on the O-ring 17c. Therefore, the influence on the O-ring 17c due to the deformation of the seal housing portion 18 can be suppressed.

  In the modification shown in FIG. 7 as well, a gap is formed between the end portion 11 h of the tube 11 and the inner surface of the reduced diameter portion 31 g of the case main body 31. Therefore, the end portion 11h of the tube 11 and the inner surface of the reduced diameter portion 31g of the case body 31 do not hit when thermally expanded.

  In addition, as in another modification shown in FIG. 8, the seal housing portion 18 includes an outer peripheral surface 10a of the laminated core 10 formed along the flow direction of the EGR gas, and a case main body 31 facing the outer peripheral surface 10a. The inner circumferential surface 31e and the end surface 11g of the bulging portion 11d of the tube 11 formed upright from the outer circumferential surface 10a of the laminated core 10 may be defined in an annular shape.

  The outer peripheral surface 10a is a flat surface (flat surface) or a smooth surface formed of a metal material such as stainless steel. Further, the end surface 11g is also a flat surface or a smooth surface formed of a metal material such as stainless steel. The O-ring 17c and the backup ring 17d are disposed between the inner peripheral surface 31e and the outer peripheral surface 10a of the case body 31.

  The outer peripheral surface 10a may be a smooth surface that has been subjected to surface lubricity treatment to improve the slipperiness.

  As described above, when the seal housing portion 18 is formed by the outer peripheral surface 10 a of the laminated core 10, the inner peripheral surface 31 e of the case body 31, and the end surface 11 g of the laminated core 10, the seal housing portion 18 is similarly housed. The shearing force does not act on the O-ring 17c. Therefore, the influence on the O-ring 17c due to the deformation of the seal housing portion 18 can be suppressed.

  Similarly, in another modified example shown in FIG. 8, a gap is formed between the end portion 11 h of the tube 11 and the inner surface of the reduced diameter portion 31 g of the case main body 31. Therefore, the end portion 11h of the tube 11 and the inner surface of the reduced diameter portion 31g of the case body 31 do not hit when thermally expanded.

  As described above, the seal housing portion 18 includes the outer peripheral surface 17e of the header member 17 or the outer peripheral surface 10a of the laminated core 10 and the outer periphery of the heat exchanging portion 1 in the heat exchanging portion 1 formed along the EGR gas flow direction. By the inner peripheral surface of the case 30 facing the surface, and the end surface 31f formed standing from the inner peripheral surface 30e of the case 30 or the end surface 11g formed standing from the outer peripheral surface of the heat exchanging portion 1 It is formed.

  Next, the operation of the heat exchanger 100 will be described.

  In the heat exchanger 100, the EGR gas guided from the supply pipe 41 flows through the tube 11 of the laminated core 10 and is discharged from the discharge pipe 42. In the heat exchanger 100, the engine cooling water supplied from the supply flow path 32 into the case body 31 flows through the flow path between the tubes 11 in the laminated core 10 and is discharged from the discharge flow path 33. Thereby, in the heat exchanger 100, heat exchange is performed between the EGR gas and the engine coolant. Since the temperature of the EGR gas is higher than the temperature of the engine coolant, the EGR gas is cooled by the engine coolant.

  According to the above 1st Embodiment, there exists an effect shown below.

  In the heat exchanger 100, the case 30 is formed of a resin material, and the laminated core 10 is formed of a metal material. As described above, since the case 30 and the laminated core 10 have different coefficients of thermal expansion, when the high-temperature EGR gas flows through the inner periphery of the tube 11, the laminated core 10 expands significantly compared to the case 30. .

  In contrast, in the heat exchanger 100, the seal housing portion 18 is formed by the outer peripheral surface 17 e of the header member 17, the inner peripheral surface 31 e of the case main body 31, and the end surface 31 f of the case main body 31. Therefore, even if the case 30 and the heat exchange part 1 have different coefficients of thermal expansion, the inner peripheral surface 31e of the case body 31 and the outer peripheral surface 17e of the header member 17 in the heat exchange part 1 slide relatively. The shape of the seal accommodating portion 18 is not changed. Therefore, the shearing force does not act on the O-ring 17c accommodated in the seal accommodating portion 18. Therefore, the influence on the O-ring 17c due to the deformation of the seal housing portion 18 can be suppressed.

  Moreover, in the heat exchanger 100, the lamination | stacking core 10 can be assembled only by laminating | stacking the some tube 11 and restraining the laminated | stacked tube 11 with the clip 20 in the lamination direction. Therefore, the heat exchanger 100 can be easily assembled.

  In the heat exchanger 100, the clips 20 have leaf spring portions 21 that elastically support the laminated core 10 with respect to the case 30 at both ends in the laminated direction of the laminated core 10. Therefore, when the laminated core 10 is thermally expanded by the high-temperature EGR gas flowing through the inner periphery of the tube 11, the leaf spring portion 21 is deformed to absorb the change in the outer shape of the laminated core 10, and the laminated core 10. Can always be held against the case 30.

(Second Embodiment)
Hereinafter, with reference to FIG. 9, the heat exchanger 200 which concerns on the 2nd Embodiment of this invention is demonstrated. In each embodiment shown below, it demonstrates centering on a different point from 1st Embodiment, the same code | symbol is attached | subjected to the structure which has the same function, and description is abbreviate | omitted.

  The heat exchanger 200 is different from the heat exchanger 100 according to the first embodiment in that the heat exchanger 200 has a case 230 divided into two.

  The heat exchanger 200 includes a laminated core 10 that exchanges heat between the EGR gas and engine cooling water, a clip 20 as a restraining member that restrains the laminated core 10 in the laminating direction, and the laminated core 10 that is housed therein. And a case 230 through which engine cooling water circulates.

  The case 230 includes a first case 231 that covers the laminated core 10 from one side, and a second case 232 that covers the laminated core 10 from the other side. The first case 231 has a flange portion 231a, and the second case 232 has a flange portion 232a. The flange portion 231a and the flange portion 232a face each other and come into contact with each other, and are fixed by bolt fastening or the like. The first case 231 and the second case 232 are formed in a funnel shape in which the diameter is gradually reduced from the portion accommodating the laminated core 10, the header member 16, and the header member 17 toward the end portions 231d and 232d. It has a reduced diameter part 231g, 232g, respectively.

  The case 230 accommodates the header member 16 and the header member 17 together with the laminated core 10. In the heat exchanger 200, the laminated core 10, the header member 16, and the header member 17 constitute the heat exchange unit 1.

  Similarly to the header member 17, the header member 16 is inserted into the inner periphery of the case 230. The cylindrical portion 16b of the header member 16 is connected to the case via an O-ring 16c as a sealing material accommodated in the seal accommodating portion 18 and a backup ring 16d as a ring member for fixing the O-ring 16c in the case 230. 230 is held on the inner periphery. Thereby, it is possible to prevent the engine coolant flowing through the case 230 from leaking into the EGR gas flow path. The cylindrical portion 16 b is connected to the supply pipe 41 through the case 230.

  Note that the configurations of the seal housing portion 18, the O-ring 16c, and the backup ring 16d are the same as those of the seal housing portion 18, the O-ring 17c, and the backup ring 17d, and thus detailed description thereof is omitted here.

  As shown in FIG. 9, between the end portion 17f of the header member 17 and the inner surface of the reduced diameter portion 232g of the second case 232, the heat exchange portion 1 is more than the case 230 due to the difference in thermal expansion coefficient. The gap is formed so that the thermal expansion can be greatly performed. Similarly, a gap is formed between the end portion 16 f of the header member 16 and the inner surface of the reduced diameter portion 231 g of the first case 231. These gaps correspond to the “range that can be moved by thermal expansion” shown in FIG. These gaps are formed larger than the difference in thermal expansion between the case 230 and the heat exchange unit 1 when the heat exchange unit 1 rises to the maximum temperature. Therefore, the end portions 16f and 17f of the header members 16 and 17 do not contact the inner surfaces of the reduced diameter portions 231g and 232g of the case 230.

  The second embodiment described above also provides the same effects as those of the first embodiment.

(Third embodiment)
Hereinafter, with reference to FIG. 10, the heat exchanger 300 which concerns on the 3rd Embodiment of this invention is demonstrated.

  The heat exchanger 300 is different from the heat exchanger 100 according to the first embodiment in that the EGR gas is not circulated in the case 330 in one direction but the EGR gas is circulated in the case 330. Is different.

  The heat exchanger 300 accommodates the laminated core 10 that exchanges heat between the EGR gas and the engine coolant, the clip 20 as a restraining member that restrains the laminated core 10 in the laminating direction, and the laminated core 10 inside. And a case 330 through which engine coolant flows. In the heat exchanger 300, the laminated core 10 and the header member 17 constitute the heat exchange unit 1.

  The tube 11 constituting the laminated core 10 has a plurality of supply tubes 11e through which EGR gas flows in the supply direction (right to left in FIG. 10), and EGR gas flows in the discharge direction (left to right in FIG. 10). A plurality of discharge tubes 11f. The plurality of supply tubes 11e are stacked together. Similarly, the plurality of discharge tubes 11f are stacked and gathered. The supply tube 11e and the discharge tube 11f, which are stacked together, are further stacked in the stacking direction (vertical direction in FIG. 10).

  A partition plate serving as a partition member for partitioning the header member 16 into a supply channel 37 and a discharge channel 38 between the supply tube 11e and the discharge tube 11f in the header member 16 to which EGR gas is supplied and discharged. 15 is provided. Although the partition plate 15 is formed in a plate shape, the partition plate 15 is not limited to the plate shape because it only needs to partition the supply channel 37 and the discharge channel 38.

  The case 330 has a case main body 331 for housing the laminated core 10. The case main body 331 is formed in a cylindrical shape so as to cover the laminated core 10 inserted from the opening 31a. The case main body 331 includes a guide portion 35 formed so as to cover the tip of the header member 17. The guide part 35 forms the direction change flow path 36 which changes the direction of the EGR gas guided from the supply tube 11e and guides it to the discharge tube 11f. The guide part 35 has a curved surface part 35g that guides the EGR gas so as to gently change the direction. The guide portion 35 may not be formed integrally with the case main body 331 but may be provided separately from the case main body 331 and attached to the case main body 331.

  As shown in FIG. 10, between the cylindrical portion 17b of the header member 17 and the inner surface of the curved surface portion 35g of the case body 331, the heat exchanging portion 1 is more than the case 330 due to the difference in thermal expansion coefficient. A gap is formed so that it can be largely thermally expanded. This gap corresponds to the “range that can be moved by thermal expansion” shown in FIG. The gap is formed larger than the difference in thermal expansion between the case 330 and the heat exchange unit 1 when the heat exchange unit 1 rises to the maximum temperature. Therefore, the cylindrical portion 17b of the header member 17 and the inner surface of the curved surface portion 35g of the case main body 331 do not hit each other.

  The third embodiment described above also provides the same effects as those of the first and second embodiments. As described above, the O-ring 17c is accommodated in the seal accommodating portion 18 in the heat exchange in which the EGR gas flows in the case 330 as well as the heat exchangers 100 and 200 in which the EGR gas flows in one direction. This is also effective in the device 300.

  As mentioned above, although embodiment of this invention was described, the said embodiment showed only a part of application example of this invention, and the meaning which limits the technical scope of this invention to the specific structure of the said embodiment. Absent.

  For example, the heat exchangers 100, 200, and 300 according to the above embodiment are not limited to EGR coolers but can be applied to heat exchangers such as charge air coolers mounted on vehicles. Moreover, it is applicable also to the heat exchanger used other than a vehicle.

  In the above embodiment, the case body 31 is formed of a material having a smaller coefficient of thermal expansion than that of the laminated core 10. You may form with a material with a big rate. Also in this case, the laminated core 10 can be always held with respect to the cases 30, 230, and 330 by providing the leaf spring portion 21 on the clip 20.

DESCRIPTION OF SYMBOLS 100 Heat exchanger 200 Heat exchanger 300 Heat exchanger 1 Heat exchange part 10 Laminated core 11 Tube 11d Expanded part 11g End surface 16 Header member 17 Header member 17a Rectangular part 17b Cylindrical part 17c O-ring (seal member)
17d Backup ring (ring member)
17e outer peripheral surface 18 seal accommodating portion 30 case 31 case main body 31e inner peripheral surface 31f end surface 230 case 231 first case 232 second case 330 case 331 case main body

Claims (6)

A heat exchanger for exchanging heat between a first fluid and a second fluid,
A heat exchange section through which the first fluid flows;
A case in which the heat exchange unit is accommodated and the second fluid flows;
An outer peripheral surface of the heat exchange unit formed along a flow direction of the first fluid, an inner peripheral surface of the case facing the outer peripheral surface of the heat exchange unit, and an inner peripheral surface of the case or the heat exchange An end surface formed upright from the outer peripheral surface of the part, and a seal housing portion defined by
A heat exchanger, comprising: a sealing material that is housed in the seal housing portion and separates the flow path of the first fluid and the flow path of the second fluid. The heat exchanger according to claim 1,
The seal housing portion is formed in an annular shape,
The heat exchanger further comprising a ring member that is press-fitted into an inner peripheral surface of the case and forms a space in which the sealing material is accommodated between the end surface. The heat exchanger according to claim 1 or 2,
The end surface defining the seal housing portion is a stepped portion formed by erecting the case from the inner peripheral surface toward the outer peripheral surface of the heat exchange unit. Heat exchanger. The heat exchanger according to any one of claims 1 to 3,
The heat exchange unit includes a plurality of stacked tubes,
A header member attached so as to cover a lower end portion in the flow direction of the first fluid in the plurality of tubes,
A flow path through which the first fluid flows is formed in each of the tubes,
A channel through which the second fluid flows is formed between the plurality of tubes,
The heat exchanger according to claim 1, wherein the seal housing part is formed by the inner peripheral surface, the end surface, and an outer peripheral surface of the header member. The heat exchanger according to any one of claims 1 to 4,
The heat exchanger, wherein the case and the case are formed of materials having different coefficients of thermal expansion. The heat exchanger according to claim 5, wherein
The heat exchange part is formed of a metal material,
The heat exchanger according to claim 1, wherein the case is made of a resin material.

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