JP2015183909A - heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger capable of reducing heat strains generated in root portions between a tank portion and tubes.SOLUTION: A heat exchanger comprises: a core section 3 in which a cooling fluid flows and that is configured by stacking a plurality of tubes 1 outside of which intake air flows; a tank section 4 aggregating or distributing the cooling fluid flowing in the tubes 1; a duct plate 5 disposed to cover the core section 3 and forming an intake channel, the duct plate 5 is joined to the tank section 4, the tank section 4 includes a tube joint surface 400 to which the tubes 1 are joined, a rib 8 extending in an intake flow direction is provided between an outermost tube 10 and the tube 1 adjacent to the outermost tube 10 on the tube joint surface 400, and the rib 8 is not provided outward, in a tube stacking direction, of the outermost tube 10 on the tube joint surface 400.

Description

  The present invention relates to a heat exchanger, and is effective when applied to an intercooler that cools combustion air (intake air) supplied to an internal combustion engine (engine).

  Conventionally, a plurality of tubes, in which the intake air circulates inside and the cooling medium circulates outside, are connected to both ends of the plurality of tubes and the intake air flowing through the plurality of tubes. An intercooler including a tank unit that performs collection or distribution is disclosed (for example, see Patent Document 1).

European Patent Application No. 1707911

  In the intercooler described in Patent Document 1, the intake air pressure loss increases because the intake air flows through the tube. For this reason, it was necessary to enlarge the flow path cross-sectional area of the tube, and there was a problem that the size of the intercooler was increased.

  On the other hand, the present inventors previously described in Japanese Patent Application No. 2013-92234 (hereinafter referred to as the prior application example) a plurality of core parts configured by laminating a plurality of tubes through which a cooling fluid flows, and a plurality of core parts. A tank part that collects or distributes the cooling fluid flowing through the tube, and a duct plate that is disposed so as to cover the core part and forms an intake passage through which intake air flows, and the duct plate is joined to the tank part. A heat exchanger is proposed.

  If the duct plate is joined to the tank portion as in the heat exchanger of the prior application, a large temperature difference is generated between the tube and the duct plate when hot intake air flows through the intake passage. Thereby, a thermal distortion may generate | occur | produce in the root part (joining part) of a tank part and a tube.

  An object of this invention is to provide the heat exchanger which can reduce the thermal distortion which generate | occur | produces in the root part of a tank part and a tube in view of the said point.

  In order to achieve the above object, in the first aspect of the present invention, the first fluid is exchanged between the first fluid that is a gas and the second fluid that is a liquid lower in temperature than the first fluid. In the heat exchanger to be cooled, a core portion (3) configured by laminating a plurality of tubes (1) through which the second fluid flows inside and the first fluid flows outside, and a plurality of tubes (1 ) And a tank part (4) that collects or distributes the second fluid flowing through the plurality of tubes (1) and a core part (3) and is arranged to cover the core part (3). And a flow path forming member (5) that forms a first fluid flow path through which the first fluid flows. The flow path forming member (5) is joined to the tank portion (4), and the tank portion (4 ) Is a tube joint surface (400) to which a plurality of tubes (1) are joined. When the tube (1) arranged on the outermost side in the stacking direction of the tubes (1) among the plurality of tubes (1) is the outermost tube (10), the tube joining surface (400) A rib (8) extending in the flow direction of the first fluid is provided between the outermost tube (10) and the tube (1) adjacent to the outermost tube (10). 400), the rib (8) is not provided outside the outermost tube (10) in the stacking direction of the tube (1).

  According to this, the rib (8) extending in the flow direction of the first fluid between the outermost tube (10) on the tube joint surface (400) and the tube (1) adjacent to the outermost tube (10). By providing, when the high temperature 1st fluid distribute | circulates to the 1st fluid flow path, the thermal load concerning the root part of a tank part (4) and a tube (1) can be disperse | distributed. Further, by not providing the rib (8) outside the outermost tube (10) in the tube joining surface (400) in the stacking direction of the tube (1), the tank (4) is formed by the rib (8). ) Can be suppressed from becoming too high and the effect of mitigating thermal strain being reduced. Therefore, it becomes possible to reduce the thermal distortion which generate | occur | produces in the root part of a tank part (4) and a tube (1).

  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.

It is a perspective view which shows the intercooler which concerns on embodiment of this invention. It is a disassembled perspective view which shows the intercooler which concerns on embodiment of this invention. It is a top view which shows the core plate vicinity in embodiment of this invention. It is a characteristic view which shows the relationship between the protrusion length of a rib, and the generated distortion ratio. It is VV sectional drawing of FIG. It is a characteristic view which shows the relationship between the distance between end surfaces, and the generated distortion ratio.

  Hereinafter, an embodiment of the present invention will be described with reference to the drawings. In this embodiment, the heat exchanger of the present invention is applied to an intercooler that cools intake air by exchanging heat between the intake air of the internal combustion engine and a cooling fluid (for example, water). Note that the intake air that is a gas corresponds to the first fluid of the present invention, and the cooling fluid that is a liquid lower in temperature than the intake air corresponds to the second fluid of the present invention.

  As shown in FIG. 1 and FIG. 2, the intercooler of this embodiment is provided with a plurality of tubes 1 for circulating a cooling fluid therein, and is disposed on both ends of the plurality of tubes 1 to circulate each tube 1. It is configured as a so-called tank-and-tube heat exchanger having a tank portion 4 and the like for collecting or distributing the cooling fluid.

  Specifically, the intercooler includes a plurality of tubes 1 through which the cooling fluid flows and the intake air flows to the outside. The tube 1 is formed in an oval shape (flat shape) with a flat vertical cross section in the longitudinal direction so that the intake flow direction (hereinafter referred to as the intake flow direction) coincides with the major axis direction.

  The plurality of tubes 1 are arranged in a row in a direction perpendicular to the flow of intake air. Further, the plurality of tubes 1 are arranged in two rows along the direction of intake air flow. That is, the plurality of tubes 1 are arranged so as to form an upstream row located upstream in the intake flow direction and a downstream row located downstream from the upstream row.

  The tube 1 has two flat surfaces that face each other across a fluid passage through which the cooling fluid flows in the tube 1. Fins (not shown) as heat transfer members formed in a wave shape are joined to the flat surfaces on both sides of the tube 1. These fins increase the heat transfer area with air to promote heat exchange between cooling water and air. Hereinafter, the substantially rectangular heat exchanging portion including the tube 1 and the fins is referred to as a core portion 3.

  The tube 1 of the present embodiment is formed by bending a single metal (for example, aluminum) plate-like member and joining the ends thereof. A sacrificial material is provided on the inner and outer surfaces of the tube 1.

  The tank portion 4 extends in a direction orthogonal to the tube longitudinal direction at both ends in the longitudinal direction of the tube 1 (hereinafter referred to as tube longitudinal direction) and communicates with the plurality of tubes 1. The tank portion 4 includes a core plate 4a having a tube joint surface 400 into which the tube 1 is inserted and joined, and a tank body portion 4b that constitutes a tank internal space together with the core plate 4a.

  Here, of the two tank parts 4, the one arranged on the upper side in the vertical direction is called a first tank part 41, and the one arranged on the lower side in the vertical direction is called a second tank part 42.

  Inside the first tank portion 41 (between the core plate 4a and the tank main body portion 4b), a separator 4c that divides the space in the tank into two in the intake flow direction is provided. Here, of the two tank spaces partitioned by the separator 4c, a space located on the downstream side of the intake flow is referred to as a first space, and a space located on the downstream side of the intake flow is referred to as a second space.

  The first space communicates with the tubes 1 belonging to the downstream row among the plurality of tubes 1 and diverts the cooling water to the tubes 1 belonging to the downstream row. The second space communicates with the tubes 1 belonging to the upstream row among the plurality of tubes 1 and collects the cooling fluid flowing out from the tubes 1 belonging to the upstream row side.

  The tank body portion 4b of the first tank portion 41 is provided with an inlet pipe 4d that allows the cooling fluid to flow into the first space, and an outlet pipe 4e that causes the cooling fluid heated by heat exchange with the intake air to flow out. ing.

  The second tank unit 42 collects the cooling fluid that has flowed out of the tubes 1 belonging to the downstream row, and diverts the collected cooling water to the tubes 1 belonging to the upstream row. Further, the second tank portion 42 extends between the core plate 4a and the tank main body portion 4b in a direction substantially orthogonal to the stacking direction of the tubes 1 (hereinafter referred to as the tube stacking direction). A plurality (two in the present embodiment) of reinforcing plates 4f that reinforce the tank portion 42 are provided.

  By configuring the two tank parts 4 (the first tank part 41 and the second tank part 42) as described above, the flow of the cooling fluid makes a U-turn in the intercooler.

  Side plates 30 that extend substantially parallel to the tube 1 and reinforce the core portion 3 are provided at both ends of the core portion 3 in the tube stacking direction. Of the side plate 30, the surface on the core portion 3 side is brazed to the fin, and both end portions in the longitudinal direction are brazed to the core plate 4 a of the tank portion 4.

  A duct plate 5 is provided outside the core portion 3 so as to cover the core portion 3 and serves as a flow path forming member that forms an intake flow path through which intake air flows. The duct plate 5 is configured by joining a first plate 51 and a second plate 52 in combination.

  The 1st plate 51 and the 2nd plate 52 are comprised with the material (in this example, aluminum) similar to other components, such as the tube 1, the fin, and the tank part 4. FIG. In addition, as a constituent material of the first plate 51 and the second plate 52, a clad material in which a brazing material is clad on at least one surface of an aluminum core material is used, thereby reducing the amount of brazing material used. Can do.

  The duct plate 5, that is, the first plate 51 and the second plate 52 are brazed and joined to the core plate 4 a of the tank unit 4 at both ends in the tube longitudinal direction.

  In the present embodiment, the first plate 51 and the second plate 52 are formed in substantially the same shape. Specifically, each of the first plate 51 and the second plate 52 is substantially orthogonal to the bottom surface 5a from both ends of the bottom surface 5a in the tube stacking direction on the bottom surface 5a that is substantially orthogonal to the intake flow direction. It is formed in a substantially U-shaped cross section having a pair of side surfaces 5b protruding in the direction and extending substantially parallel to the intake flow direction. The side surface 5 b is brazed to the side plate 30.

  Openings 5 c are formed on the bottom surfaces 5 a of the first plate 51 and the second plate 52 to allow the intake air to flow into and out of the intake flow path in the duct plate 5. In the present embodiment, the opening 5c is formed over substantially the entire bottom surface 5a. Further, a wall portion 5d extending toward the opposite side to the core portion 3 is provided at the outer peripheral edge portion of the opening portion 5c.

  A connection plate 7 for connecting an intake air flow path of the intercooler and an intake duct (not shown) is joined to each opening 5c of the first plate 51 and the second plate 52. That is, the intake duct is connected to the opening 5 c of each of the first plate 51 and the second plate 52 via the connection plate 7.

  By joining the side surfaces 5b of the first plate 51 and the second plate 52 configured as described above, a duct plate 5 having a rectangular cross section is formed.

  Here, among the plurality of tubes 1, the tube 1 disposed on the outermost side in the tube stacking direction is referred to as the outermost tube 10.

  As shown in FIG. 3, a rib 8 extending in the intake flow direction is provided between the outermost tube 10 and the tube 1 adjacent to the outermost tube 10 on the tube joint surface 400 of the core plate 4a. . The rib 8 is formed so as to protrude from the tube joining surface 400 toward the inside in the tube longitudinal direction (the core portion 3 side, the paper surface side in FIG. 3). In the present embodiment, ribs 8 are also provided between adjacent tubes 1 on the tube joint surface 400.

  On the other hand, the rib 8 is not provided in the portion 410 of the tube joining surface 400 outside the outermost tube 10 in the tube stacking direction. That is, in this embodiment, the rib 8 is provided between the adjacent tubes 1 (including the outermost tube 10) among the tube joint surfaces 400, and the rib 8 is provided at other portions. Absent.

  The rib 8 protrudes in the intake flow direction with respect to the outermost tube 10. Hereinafter, the part which protrudes with respect to the outermost tube 10 among the ribs 8 is called the protrusion part 80. FIG. The length of the protrusion 80 in the intake flow direction is referred to as a protrusion length La. In the present embodiment, the protruding lengths La of the plurality of ribs 8 are equal to each other.

  Here, the relationship between the protrusion length La of the protrusion 80 and the thermal strain generated at the root portion between the core plate 4a and the tube 1 is shown in FIG. The generated strain ratio shown on the vertical axis in FIG. 4 is that the protrusion length La of the protrusion 80 is 0, that is, the end of the outermost tube 10 and the end of the rib 8 when viewed from the tube stacking direction. It is a value of thermal strain expressed as 100% of thermal strain generated when polymerization is performed.

  As shown in FIG. 4, by setting the protrusion length La of the rib 8 to 1.2 mm or more, the core plate 4 a and the tube 1 are attached to each other as compared with the case where the protrusion length La of the protrusion 80 is zero. The thermal strain generated in the part can be reduced by about 10%. Furthermore, by setting the protrusion length La of the rib 8 to 1.8 mm or more, heat generated at the root portion between the core plate 4a and the tube 1 compared to the case where the protrusion length La of the protrusion 80 is zero. The distortion can be reduced by about 15%.

  Hereinafter, the surface of the core plate 4 a to which the duct plate 5 is bonded is referred to as a plate bonding surface 43. As shown in FIG. 5, the shortest distance in the intake flow direction from the end surface 100 in the intake flow direction of the tube 1 to the end surface 430 in the intake flow direction of the plate joint surface 43 is referred to as an end surface distance Lb.

  In the present embodiment, the end face distance Lb represents the shortest distance in the intake flow direction from the end face 100 of the tube 1 in the intake flow direction to the end face 430 of the plate joint surface 43 perpendicular to the intake flow direction. ing.

  Here, FIG. 6 shows the relationship between the distance Lb between the end faces and the thermal strain generated at the root portion between the core plate 4 a and the tube 1. Note that the generated strain ratio shown on the vertical axis in FIG. 6 is a value of thermal strain expressed as 100% of the thermal strain generated when the distance Lb between the end faces is 2 mm, which is the manufacturing limit.

  As shown in FIG. 5, by setting the distance Lb between the end faces to 4.9 mm or more, the thermal strain generated at the root portion between the core plate 4a and the tube 1 is reduced as compared with the case where the distance Lb between the end faces is 2 mm. It can be reduced by about 40%. Further, by setting the distance Lb between the end faces to 6.6 mm or more, the thermal strain generated at the root portion between the core plate 4a and the tube 1 is reduced by about 50% compared to the case where the distance Lb between the end faces is 2 mm. be able to.

  As described above, in the present embodiment, the rib 8 extending in the intake flow direction is provided between the outermost tube 10 on the tube joint surface 400 of the core plate 4a and the tube 1 adjacent to the outermost tube 10. Yes. Thereby, when high-temperature intake air flows through the intake flow path, the thermal load applied to the root portion of the core plate 4a and the tube 1 can be dispersed, so that thermal distortion can be reduced.

  By the way, when the rib 8 is provided on the tube joining surface 400, the rigidity of the core plate 4a is increased, so that the restraining force against the thermal expansion / shrinkage of the tube 1 in the vicinity of the rib 8 of the core plate 4a is increased. This may reduce the relaxation effect.

  On the other hand, in this embodiment, the rib 8 is not provided outside the outermost tube 10 in the tube joining surface 400 in the tube stacking direction. Thereby, since it can suppress that the rigidity of the core plate 4a becomes high too much by providing the rib 8, the restraint force with respect to the thermal expansion and thermal contraction of the tube 1 in the core plate 4a can be reduced. As a result, the thermal stress generated at the root portion between the core plate 4a and the tube 1 can be reduced.

  At this time, as shown in FIG. 4 described above, by setting the protruding length La of the rib 8 to 1.2 mm or more, it is possible to reduce thermal distortion generated at the root portion between the core plate 4a and the tube 1. . Furthermore, the thermal distortion which generate | occur | produces in the root part of the core plate 4a and the tube 1 can be reduced more because the protrusion length La of the rib 8 shall be 1.8 mm or more.

  Moreover, as shown in the above-mentioned FIG. 6, the thermal distortion which generate | occur | produces in the root part of the core plate 4a and the tube 1 can be reduced because the distance Lb between end surfaces shall be 4.9 mm or more. Furthermore, the thermal distortion which generate | occur | produces in the root part of the core plate 4a and the tube 1 can be reduced more because the distance Lb between end surfaces shall be 6.6 mm or more.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention.

  (1) In the above embodiment, the example in which the ribs 8 are provided between the adjacent tubes 1 on the tube joining surface 400 has been described, but the present invention is not limited to this. That is, if the rib 8 is provided between the outermost tube 10 and the tube 1 adjacent to the outermost tube 10, the rib 8 may not be provided between the adjacent tubes 1 other than the outermost tube 10. .

  (2) In the above-described embodiment, the example in which the protruding lengths La of the plurality of ribs 8 provided on the tube joint surface 400 are equal to each other has been described. The protruding lengths La of the plurality of ribs 8 may be different from each other. In this case, if the protruding length La of the rib 8 between the outermost tube 10 and the tube 1 adjacent to the outermost tube 10 is set in the range described in the above embodiment, the portion other than the outermost tube 10 is used. The protruding length La of the rib 8 between the adjacent tubes 1 may be arbitrarily set.

  (2) In the above-described embodiment, the example in which the flow of the cooling fluid is configured to make a U-turn in the intercooler has been described. However, the present invention is not limited thereto, and the configuration may be such that the flow of the cooling fluid does not turn. The cooling fluid flow may be W-turned (three U-turns).

1 Tube 3 Core part 4 Tank part 5 Duct plate (flow path forming member)
8 Rib 10 Outermost tube 400 Tube joint surface

Claims (6)

A heat exchanger that cools the first fluid by performing heat exchange between a first fluid that is a gas and a second fluid that is a liquid lower in temperature than the first fluid,
A core portion (3) configured by laminating a plurality of tubes (1) through which the second fluid flows and the outside flows through the first fluid;
A tank portion (4) connected to at least one end of the plurality of tubes (1) and collecting or distributing the second fluid flowing through the plurality of tubes (1);
A flow path forming member (5) disposed so as to cover the core portion (3) and forming a first fluid flow path through which the first fluid flows;
The flow path forming member (5) is joined to the tank part (4),
The tank part (4) has a tube joining surface (400) to which the plurality of tubes (1) are joined,
Among the plurality of tubes (1), when the tube (1) disposed on the outermost side in the stacking direction of the tubes (1) is the outermost tube (10),
A rib (8) extending in the flow direction of the first fluid between the outermost tube (10) and the tube (1) adjacent to the outermost tube (10) on the tube joining surface (400). )
The heat exchanger, wherein the rib (8) is not provided outside the outermost tube (10) in the stacking direction of the tube (1) in the tube joining surface (400).   The heat exchanger according to claim 1, wherein the rib (8) protrudes in the flow direction of the first fluid with respect to the outermost tube (10).   The protruding length (La), which is the length in the flow direction of the first fluid, in the portion (80) protruding from the outermost tube (10) of the rib (8) is 1.2 mm or more. The heat exchanger according to claim 2, wherein the heat exchanger is provided.   The heat exchanger according to claim 3, wherein the protruding length (La) is 1.8 mm or more. The tank part (4) includes a core plate (4a) having the tube joint surface (400), and a tank body part (4b) that constitutes a tank internal space together with the core plate (4a).
The flow path forming member (5) is joined to the core plate (4a),
Of the surface (43) of the core plate (4a) to which the flow path forming member (5) is joined from the end surface (100) of the tube (1) in the flow direction of the first fluid, The distance (Lb) between the end faces, which is the shortest distance in the flow direction of the first fluid, to the end face (430) in the flow direction is 4.9 mm or more. The heat exchanger described in 1.   The heat exchanger according to claim 5, wherein the distance between the end faces (Lb) is 6.6 mm or more.

Images