JP2007078292A - Heat exchanger, and dual type heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger, and a dual type heat exchanger capable of reducing the flow resistance of an internal fluid, while properly securing cooling performance. <P>SOLUTION: The heat exchanger has a plurality of tubes 211, and one pair of header tanks 220, 230. It is provided with a pipe 240 having a passage cross sectional area almost the same as a pipe arrangement, arranged at one outer side in the laminating direction of the tubes 211, and communicated with interiors of the pair of header tanks 220, 230, and a partition part 250 arranged in a boundary between the tube 211 and the pipe 240 in one header tank 220, and having an opening 251 becoming predetermined resistance when the fluid passes. An inflow part 261 is communicated with one of a space in a tube 211 side or a space in a pipe 240 side with respect to the partition part 250 in one header tank 220, and an outflow part 262 is communicated with the opposite side. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention is a heat exchanger suitable for use in, for example, an oil cooler that cools vehicle engine oil or ATF (automatic transmission fluid), and other heat such as a condenser for a cooling device. The present invention relates to a dual heat exchanger in which an exchanger is integrally provided.

  As a conventional heat exchanger, for example, the one shown in Patent Document 1 is known. That is, this heat exchanger is widely used as a radiator, an oil cooler, a condenser, etc., and fins are interposed between a plurality of stacked tubes to form a core portion. And the both ends of a some tube are connected to a pair of tank part, and the tube and the tank part are connecting.

An internal fluid (cooling water, oil, refrigerant, etc.) flows from one tank portion, and the internal fluid flows out from the other tank portion after flowing through the plurality of tubes. Further, cooling air is supplied to the outside of the core portion so that the internal fluid is cooled by heat exchange with the cooling air. In such a heat exchanger, the size of the cooling performance can be set according to the length of the tube, the number of laminated tubes, the specifications of the fins, and the like.
JP 2004-293878 A

  However, in the heat exchanger as described above, if you want to set the cooling performance small by keeping the tube length from the other party's mounting conditions, etc., if you reduce the number of tubes, the flow cross-sectional area of the internal fluid will be small. The flow resistance of the internal fluid in the core portion is greatly increased, and the originally expected cooling performance cannot be obtained. Therefore, when the number of tubes is increased in order to reduce the flow resistance, naturally, too much cooling performance is obtained, leading to overcooling of the internal fluid.

  In view of the above problems, an object of the present invention is to provide a heat exchanger and a dual heat exchanger that can reduce the flow resistance of an internal fluid while appropriately ensuring cooling performance.

  In order to achieve the above object, the present invention employs the following technical means.

  In the first aspect of the present invention, a plurality of laminated layers are connected to the tube (211) in which the fluid supplied from the piping circulates, and to both ends in the longitudinal direction of the tube (211). In the heat exchanger having a pair of header tanks (220, 230) communicating with each other, the heat exchanger has a flow passage cross-sectional area similar to that of the pipe, and is disposed on one outer side in the stacking direction of the tubes (211). The pipe (240) communicating with the pair of header tanks (220, 230) and the tube (211) and the pipe (240) in one header tank (220) of the pair of header tanks (220, 230). And a partition part (250) having an opening (251) having a predetermined resistance when the fluid passes through, and an inflow part (261) into which the fluid flows Of the outflow portion (262) flowing out to the outside, the space where the inflow portion (261) is on the tube (211) side with respect to the partition portion (250) in one header tank (220) and the pipe (240) side The outflow part (262) is communicated with the opposite side to any one of the spaces, or the space where the inflow part (261) is on the tube side and the other header tank (230), The outflow part (262) is communicated with the opposite side.

  Thereby, the inflow part (261) is arranged in one header tank (220) with respect to the partition part (250), either the space on the tube (211) side or the space on the pipe (240) side, the outflow part ( When 262) is connected to the opposite side, the fluid flows in a U-turn through the plurality of tubes (211) and pipes (240). The flow resistance of the fluid in the pipe (240) is equivalent to the flow resistance of the pipe. Also, in one header tank (220), a predetermined amount of fluid out of the total flow rate passes through the opening (251) of the partition part (250) and does not flow through the plurality of tubes (211), but the inflow part (261). ) Directly flows into the outflow part (262). That is, since the flow rate of the fluid flowing through the plurality of tubes (211) can be reduced by a predetermined amount with respect to the total flow rate of the fluid supplied to the heat exchanger (200), heat exchange in the plurality of tubes (211) is performed. Fluid flow resistance can be reduced while adequately ensuring performance.

  In addition, when the inflow part (261) communicates with either the space on the tube side with respect to the partition part (250) and the other header tank (230), the outflow part (261) communicates with the opposite side. , Fluid flows in parallel through a plurality of tubes (211) and pipes (240). At this time, the flow rate of the fluid flowing through the pipe (240) by the opening (251) of the partition (250) is reduced to a predetermined amount out of the total flow rate. That is, similarly to the above, the flow rate of the fluid flowing through the plurality of tubes (211) can be reduced by a predetermined amount with respect to the total flow rate of the fluid supplied to the heat exchanger (200). The fluid flow resistance can be reduced while appropriately ensuring the heat exchange performance in 211).

  The invention according to claim 2 is characterized in that a curved portion (241) that absorbs thermal strain in the longitudinal direction is formed in an intermediate portion of the pipe (240).

  Thereby, the stress which generate | occur | produces in the connection part of a some tube (211) and a header tank (220,230) by a thermal strain, and the connection part of a pipe (240) and a header tank (220,230) is reduced. Therefore, it is possible to prevent breakage at each connecting portion.

  The invention according to claim 3 relates to a dual heat exchanger, and the heat exchanger (200) according to claim 1 or claim 2 and another tube in which another fluid different from the fluid flows ( 111) and another heat exchanger (100) formed by connecting a pair of other header tanks (120, 130) to both ends in the longitudinal direction of the other tube (111). The other header tanks (120, 130) are connected to the header tanks (220, 230) so that the respective stacked states of the tubes (211) and the other tubes (111) are continuous. The heat exchanger (100) is formed integrally with the heat exchanger (200).

  Thereby, it has the heat exchanger (200) which has the merit of Claim 1 or Claim 2, enables heat exchange with respect to two fluids, and is set as the double-type heat exchanger (10) excellent in mounting property. be able to.

  The invention according to claim 4 is characterized in that the tube (211) and the other tube (111) have the same specifications.

  Thereby, it becomes unnecessary to sort the tube (211) and the other tube (111), and the productivity when forming the core portion (210, 110) as the dual heat exchanger (10) can be increased.

  In the invention according to claim 5, the temperature of the fluid and the other fluid is different, and both the fluid and the other fluid flow between the heat exchanger (200) and the other heat exchanger (100). This is characterized in that a dummy tube (311) in which is prevented is interposed.

  Thereby, since the dummy tube (311) becomes a heat insulation part and the heat transfer between the heat exchanger (200) and another heat exchanger (100) can be prevented, each heat exchanger (100, 200). The heat effect between can be eliminated.

  The invention according to claim 6 is characterized in that the tube (211), the other tube (111), and the dummy tube (311) have the same specifications.

  As a result, as in the invention described in claim 4, it is not necessary to sort the tube (211), the other tube (111), and the dummy tube (311), and the core portion as the dual heat exchanger (10) ( 210, 110) can be made more productive.

  In the invention according to any one of claims 3 to 6, as in the invention according to claim 7, the dual heat exchanger is disposed in the vehicle engine room, and comprises a heat exchanger (200). Is an oil cooler (200) that cools the ATF for a vehicle automatic transmission, and the other heat exchanger (100) is suitable as a refrigerant condenser (100) that condenses and liquefies the refrigerant of the vehicle refrigeration system.

  In addition, the code | symbol in the bracket | parenthesis of each said means shows a corresponding relationship with the specific means of embodiment description mentioned later.

(First embodiment)
The first embodiment of the present invention includes an oil cooler 200 as a heat exchanger that cools an ATF (automatic match transmission fluid) of an automatic transmission for an automobile, and a refrigeration cycle of an air conditioner for an automobile as another heat exchanger. This is a dual heat exchanger 10 integrally formed with a refrigerant condenser 100 for condensing and liquefying the refrigerant. First, the overall configuration will be described with reference to FIGS. 1 and 2. 1 is a front view showing the entire duplex heat exchanger 10, and FIG. 2 is a cross-sectional view showing the separator 250 when viewed from the direction A in FIG.

  As is well known, the refrigeration cycle includes a closed circuit in which a compressor, a refrigerant condenser 100, an expansion valve, an evaporator, and the like are sequentially connected by refrigerant piping. The refrigerant condenser 100 is placed in a header tank 120, 220, 230, and a modulator 140 so that the refrigerant condenser 100 is located in a location that is susceptible to traveling air (cooling air) in an automobile engine room, usually on the front side of the engine cooling radiator. It is attached to the vehicle body via a mounting bracket 270 provided on the vehicle body. In addition, cooling air is supplied to the core parts 110 and 210, which will be described later, from the front side to the back side of the paper surface in FIG. 1 by running air and a blower (not shown).

  The refrigerant condenser 100 includes a core portion 110, a right header tank (corresponding to another header tank in the present invention) 120, a left header tank (corresponding to another header tank in the present invention) 130, a modulator 140, and the like. . Each member described below is made of aluminum or an aluminum alloy, and is assembled by fitting, caulking, jig fixing, or the like, and is brazed integrally with a brazing material provided in advance on a necessary portion of each member surface.

  The core portion 110 includes a plurality of tubes (corresponding to other tubes in the present invention) 111 through which a refrigerant (another fluid in the present invention) flows, and a plurality of fins that expand the heat radiation area and improve the heat exchange performance. 112 are alternately laminated, and a side plate 113 as a strength member is disposed further outward of the lowermost outermost fin 112.

  The tube 111 has a flat cross section perpendicular to the longitudinal direction, and a plurality of internal flow paths partitioned by a plurality of partition walls, and is formed by, for example, extrusion. The fin 120 is a corrugated fin formed in a corrugated shape from a thin strip plate material by roller processing. The side plate 113 has a U-shaped cross section at the general portion and is open on the side opposite to the tube. Moreover, the longitudinal direction edge part is plate-shaped for joining with the header tanks 120 and 130 mentioned later. Hereinafter, the stacking direction of the tubes 111 will be referred to as the up-down direction and the longitudinal direction of the tubes 111 will be referred to as the left-right direction based on FIG.

  Furthermore, the core part 110 is divided into a condensing part 110A on the upper side and a subcooling part 110B on the lower side. The condensing unit 110A is composed of a first tube group 111A having a predetermined number of the stacked tubes 111, and the supercooling unit 110B is composed of the remaining second tube group 111B. Here, the number of stacked layers of the second tube group 111B (supercooling unit 110B) is set to be smaller than the number of stacked layers of the first tube group 111A (condensing unit 110A).

  A pair of header tanks (the right header tank 120 and the left header tank 130) extending in the vertical direction are provided on the left and right parts of the core part 110 (both ends in the longitudinal direction of the plurality of tubes 111). Both header tanks 120 and 130 are cylindrical bodies having a substantially circular cross section, and are formed by joining a header plate and a tank plate having a semicircular cross section.

  The header tanks 120 and 130 are provided with a plurality of tube holes (not shown), and both end portions in the longitudinal direction of the tubes 111 are fitted into the tube holes so that the tubes 111 and the header tanks 120 and 130 communicate with each other. To be connected. Further, the longitudinal end portions of the side plates 113 are also fitted and connected to plate holes (not shown) provided in both header tanks 120 and 130.

  The header caps 150 are provided at the openings 121 and 131 at both ends in the longitudinal direction of the header tanks 120 and 130, and the openings 121 and 131 are closed by the header cap 150.

  The header tanks 120 and 130 are provided with separators 122, 123, 124, 132, 133, and 134 for partitioning the internal space, respectively. The header tanks 120 and 130 are each divided into three spaces by the separators 122 to 124 and 132 to 134.

  Here, the separators 122 and 132 are provided on the side opposite to the header cap (150) in the refrigerant condenser 100, and close the end side as the header tanks 120 and 130. Separator 123,133 is provided in the position corresponding to the boundary part of the condensation part 110A and the subcooling part 110B in both header tanks 120,130. The separator 124 is provided between the separator 122 and the separator 123, and the separator 134 is provided between the separator 132 and the separator 133. The separator 124 is disposed at a position above the separator 134.

  An inlet joint 161 is provided between the separator 122 and the separator 124 of the right header tank 120, and the inlet joint 161 communicates with the upper space in the right header tank 120. An outlet joint 162 is provided between the header cap 150 of the right header tank 120 and the separator 123 so that the outlet joint 162 communicates with a lower space in the right header tank 120.

  A modulator 140 is provided on the counter tube side of the left header tank 130. The modulator 140 is a receiver that separates the refrigerant from the condensing unit 110A into gas-liquid two phases and outflows the liquid-phase refrigerant out of the gas-liquid two phases to the supercooling unit 110B. That is, the modulator 140 is a container body formed by attaching a cap 141 and a screw cap 142 to both ends in the longitudinal direction of the cylindrical main body, and the interior of the modulator 140 is the middle space in the left header tank 130. And the left header tank 130 so as to communicate with the lower space. A modulator 140 is provided with a desiccant 143 and a filter 144 for removing moisture and foreign matter that have entered the refrigeration cycle.

  The oil cooler 200 is formed above the refrigerant condenser 100, and includes a core portion 210, a right header tank (a header tank in the present invention, corresponding to one header tank) 220, a left header tank (a header tank in the present invention). , Corresponding to the other header tank). Each member constituting the oil cooler 200 is also made of aluminum or an aluminum alloy similarly to the refrigerant condenser 100, and is assembled by fitting, caulking, fixture fixing, etc., and provided in advance at necessary portions on the surface of each member. The material is brazed together with the refrigerant condenser 100.

  The core portion 210 includes a plurality of tubes 211 in which ATF (fluid in the present invention) flows, and a plurality of fins 212 that increase the heat radiation area to improve heat exchange performance, and are stacked on the outermost side. A side plate 213 as a strength member is disposed further outward of the fin 212.

  The tubes 211, fins 212, and side plates 213 for the oil cooler 200 have the same specifications as the tubes 111, fins 112, and side plates 113 for the refrigerant condenser 100, respectively. The stacking direction of the tubes 211 is set to be the same as the stacking direction of the tubes 111. That is, the tube 211 is continuously stacked on the tube 111 on the upper side of the tube 111.

  A dummy tube 311 is interposed between the core portion 110 and the core portion 210, that is, between the tube 111 and the tube 211. The dummy tube 311 has the same specifications as the tube 111. The dummy tube 311 is disposed above the positions of the separators 122 and 132 in both header tanks 120 and 130 of the refrigerant condenser 100.

  A pair of header tanks (right header tank 220, right header tank 220, extending upward from both header tanks 120, 130 for the refrigerant condenser 100 are formed on the left and right parts of the core part 210 (both longitudinal ends of the plurality of tubes 211). A left header tank 230) is provided. In both header tanks 220 and 230, separators 221 and 311 are provided at positions between the dummy tube 311 and the lowermost tube 211, respectively. Thereby, internal spaces as header tanks 220 and 230 are formed between the separator 221 and the header cap 150 and between the separator 231 and the header cap 150, respectively.

  A plurality of tube holes (not shown) are formed in both the header tanks 220 and 230, and both longitudinal ends of the respective tubes 211 are fitted into the tube holes, so that the tubes 211 and the header tanks 220 and 230 communicate with each other. To be connected. Further, the longitudinal end portions of the side plates 213 are also fitted and connected to plate holes (not shown) provided in the header tanks 220 and 230.

  Note that a space between the separator 122 and the separator 221 and between the separator 132 and the separator 231 is a space where neither the refrigerant nor the ATF flows. Accordingly, the dummy tube 311 is not filled with the refrigerant and ATF, but is filled with only air.

  On the upper side of the core portion 210 (one outer side in the stacking direction of the tubes 211), pipes 240 are disposed along the inside of the U-shaped cross section of the side plate 213, and both end portions in the longitudinal direction are The header tanks 220 and 230 communicate with each other. The pipe 240 is a pipe having a circular cross section, has a flow path cross-sectional area similar to that of an ATF vehicle pipe (not shown), and has a curved portion 241 that curves upward at the middle portion.

  In the right header tank 220, a separator 250 is provided at a position between the uppermost tube 211 and the pipe 240 as a partition that partitions the space in the right header tank 220. Further, a hole 251 serving as an opening through which a predetermined amount of ATF flows is formed in the central portion of the separator 250 as a predetermined resistance when the ATF passes (FIG. 2).

  An inlet pipe 261 as an ATF inflow portion is provided between the header cap 150 and the separator 250 of the right header tank 220 so that the inlet pipe 261 communicates with the upper space in the right header tank 220. Yes. Further, an outlet pipe 262 as an ATF outflow portion is provided between the separator 221 and the separator 250 of the right header tank 220 so that the outlet pipe 262 communicates with a lower space in the right header tank 220. Yes.

  Next, the operation and effect of the dual heat exchanger 10 configured as described above will be described.

  In the refrigerant condenser 100, the inlet joint 161 is connected to the discharge side of a compressor (not shown), and the outlet joint 162 is connected to an expansion valve (not shown). Refrigerant (for example, 60 ° C.) discharged from the compressor flows into the space above the right header tank 120 from the inlet joint 161, and the first tube group 111A (condensing unit 110A) is separated by the separators 123, 124, 133, and 134. It flows in an S-shape and is condensed and liquefied by heat exchange with cooling air.

  Further, the refrigerant flows into the middle space of the left header tank 130 and flows into the modulator 140. In the modulator 140, the refrigerant is separated into gas-liquid two phases, and only the liquid-phase refrigerant out of the gas-liquid two phases passes through the space below the left header tank 130, and the second tube group 111B (supercooling unit 110B). And is supercooled by the cooling air. Then, the supercooled refrigerant flows out from the outlet joint 162 through the space below the right header tank 120 and reaches the expansion valve.

  On the other hand, in oil cooler 200, inlet pipe 261 is connected to an ATF outlet portion of an automatch transmission (not shown) by a vehicle pipe, and outlet pipe 262 is an ATF inlet portion of an automatch transmission (not shown) and a vehicle pipe. Connected by. ATF (for example, 150 ° C.) discharged from the ATF outlet portion flows into the space above the right header tank 220 from the inlet pipe 261 through the vehicle piping. Most of the ATF in the total flow rate flows in a U-turn in the order of the pipe 240, the left header tank 230, and the tube 211 by the partition of the separator 250, and the space below the right header tank 220, the outlet pipe 262, the vehicle It reaches the ATF inlet through the piping for construction. The ATF is cooled by cooling air when flowing through the tube 211. The flow resistance of ATF in the pipe 240 is equivalent to the flow resistance of the vehicle piping.

  Further, a predetermined amount (for example, 20%) of the ATF flowing into the space above the right header tank 220 passes through the hole 251 of the separator 250 and flows through the space below the right header tank 220. It flows out from the outlet pipe 262 and reaches the ATF inlet through the vehicle piping.

  As described above, in the present embodiment, the flow rate of ATF flowing through the tube 211 can be reduced by a predetermined amount by the separator 250 having the holes 251 with respect to the total flow rate of ATF supplied to the oil cooler 200. While ensuring the heat exchange performance in the tube 211 appropriately, the distribution | circulation resistance of ATF can be reduced.

  Further, since the pipe 240 is disposed on one outer side in the stacking direction of the tubes 211, the contribution of heat exchange to the ATF is extremely small. Therefore, a temperature difference occurs between the tube 211 and the pipe 240, and even if a thermal strain occurs in the longitudinal direction of the pipe 240 with respect to the tube 211 due to this temperature difference, it can be absorbed by the curved portion 241. The stress generated at the connection portion between the header tanks 220 and 230 and the connection portion between the pipe 240 and the header tanks 220 and 230 can be reduced, and breakage at each connection portion can be prevented.

  Further, since the oil cooler 200 having the pipe 240 and the separator 250 and the refrigerant condenser 100 are integrally formed so that the tube 211 is continuously laminated on the tube 111, the oil cooler 200 is formed in the longitudinal direction of the vehicle. The composite heat exchanger 10 can be made compact, has excellent mountability, and enables heat exchange with respect to two fluids (ATF, refrigerant).

  Further, since the tube 111, the tube 211, and the dummy tube 311 all have the same specification (the fins 112 and 212 and the side plates 113 and 213 also have the same specification), the tube 111, the tube 211, and the dummy tube 311 are sorted. Therefore, the productivity when forming the core portions 110 and 210 as the dual heat exchanger 10 can be increased. That is, the core portions 110 and 210 can be easily formed by continuously laminating one type of tube (111). Also, when the end of the tube (111) in the longitudinal direction is inserted into the tube hole and connected to the header tanks 120, 130, 220, 230, the insertion force ( (Fitting force) can be made uniform, and assembly work can be facilitated.

  Further, since both the inlet pipe 261 and the outlet pipe 262 of the oil cooler 200 are provided on the right header tank 220 side, both the vehicle pipes can be arranged close to each other and the assembly work is facilitated. be able to.

  Further, since the dummy tube 311 is interposed between the core part 110 and the core part 210, the dummy tube 311 serves as a heat insulating part between the ATF and the refrigerant having different temperatures, and the oil cooler 200 and the refrigerant. Heat transfer between the condenser 100 and the oil cooler 200 and the refrigerant condenser 100 can be eliminated.

(Second Embodiment)
A second embodiment of the present invention is shown in FIG. 2nd Embodiment changes the setting position of the inlet pipe 261 and the outlet pipe 262 in the oil cooler 200 with respect to the said 1st Embodiment.

  That is, here, the inlet pipe 261 is provided so as to communicate with the left header tank 230, and the outlet pipe 262 is provided in a lower space in the right header tank 220 (a space on the tube 211 side with respect to the separator 250). It is arranged to communicate.

  Thereby, in the oil cooler 200, the ATF flowing from the inlet pipe 261 flows through the tube 211 and the pipe 240 in parallel. At this time, the flow rate of ATF flowing through the pipe 240 through the hole 251 of the separator 250 is reduced to a predetermined amount out of the total flow rate. That is, as in the first embodiment, the ATF flow rate flowing through the tube 211 can be reduced by a predetermined amount with respect to the total flow rate of ATF supplied to the oil cooler 200. While ensuring adequately, the flow resistance of fluid can be reduced.

(Third embodiment)
A third embodiment of the present invention is shown in FIG. 3rd Embodiment changes the setting position of the separator 250 in the oil cooler 200 with respect to the said 2nd Embodiment.

  That is, the separator 250 is provided in the left header tank 230 at a position between the uppermost tube 211 and the pipe 240.

  Thereby, in the oil cooler 200, the ATF flowing from the inlet pipe 261 flows through the tube 211. In addition, ATF that is throttled to a predetermined amount out of the total flow rate by the hole 251 of the separator 250 flows through the pipe 240. Therefore, similarly to the second embodiment, the flow rate of ATF flowing through the tube 211 can be reduced by a predetermined amount with respect to the total flow rate of ATF supplied to the oil cooler 200. While ensuring adequately, the flow resistance of fluid can be reduced.

(Fourth embodiment)
A fourth embodiment of the present invention is shown in FIG. 4th Embodiment replaces the setting position of the inlet pipe 261 and the outlet pipe 262 with respect to the said 1st Embodiment.

  Here, ATF flows from the inlet pipe 261 into the space below the right header tank 220. Most of the ATF in the entire flow rate flows in a U-turn in the order of the tube 211, the left header tank 230, and the pipe 240 by the partition of the separator 250, and flows out from the outlet pipe 262 through the space above the right header tank 220. To do.

  Furthermore, out of the ATF flowing into the space below the right header tank 220, a predetermined amount (for example, 20%) of ATF passes through the hole 251 of the separator 250 and flows into the space above the right header tank 220, It flows out from the outlet pipe 262.

  Therefore, similarly to the first embodiment, the separator 250 can reduce the ATF flow rate through the tube 211 by a predetermined amount with respect to the total flow rate of ATF supplied to the oil cooler 200. ATF distribution resistance can be reduced while adequately ensuring heat exchange performance.

(Fifth embodiment)
A fifth embodiment of the present invention is shown in FIG. 5th Embodiment changes the setting position of the refrigerant condenser 100 and the oil cooler 200 with respect to the said 4th Embodiment.

  In the present embodiment, the arrangement of the two heat exchangers in the vertical direction is changed according to the routing position of the vehicle piping of the oil cooler 200, and the oil cooler 200 is located below the refrigerant condenser 100.

  The oil cooler 200 is a vertically inverted version of that of the fourth embodiment. Moreover, the core part 110 of the refrigerant | coolant condenser 100 has arrange | positioned the supercooling part 110B above the condensation part 110A. Note that a suction pipe 145 is provided in the modulator 140, and the suction section 145 connects the condensing part 110 </ b> A and the supercooling part 110 </ b> B.

  Thereby, the effect similar to the said 4th Embodiment can be acquired. In addition, the oil cooler 200 can be arranged according to the vehicle piping.

(Other embodiments)
In each of the embodiments described above, the dual heat exchanger 10 in which the oil cooler 200 and the refrigerant condenser 100 are integrally formed has been described. However, the pipe 240 and the separator 250 reduce the ATF flow resistance. For example, the oil cooler 200 may be used alone. Further, instead of the oil cooler 200, a radiator, an intercooler, an engine oil cooler, or the like, or a heat exchanger other than for a vehicle may be used.

  The bending portion 241 of the pipe 240 may be set according to the state of occurrence of thermal strain, and may be unnecessary (as a straight pipe) when there is no risk of malfunction due to thermal strain.

  Further, the opening of the separator 250 is not limited to the hole 251 opened in the center of the separator 250, but the end side of the separator 250 is cut by a predetermined area so as to be a gap formed between the inner wall of the header tank. Anyway.

  Moreover, in the duplex heat exchanger 10, although the assembling property of the core portion is inferior, each tube 111, 211 may be set as a dedicated tube specification suitable for each in order to bring out each cooling performance. good.

  The dummy tube 311 may also be set according to the degree of thermal influence between the two heat exchangers.

  Moreover, although demonstrated as the double heat exchanger 10 in which the oil cooler 200 and the refrigerant | coolant condenser 100 are integrally formed, as a heat exchanger used as object, a radiator, an intercooler, an engine oil cooler, etc., Furthermore, a heat exchanger other than for vehicles may be used.

It is a front view which shows the whole double heat exchanger in 1st Embodiment. It is sectional drawing which shows the separator at the time of seeing from the A direction of FIG. It is a front view which shows the whole double heat exchanger in 2nd Embodiment. It is a front view which shows the whole double heat exchanger in 3rd Embodiment. It is a front view which shows the whole duplex heat exchanger in 4th Embodiment. It is a front view which shows the whole double heat exchanger in 5th Embodiment.

Explanation of symbols

10 Duplex Heat Exchanger 100 Refrigerant Condenser 110 Core Part 111 Tube (Other Tubes)
120 Right header tank (other header tanks)
130 Left header tank (other header tanks)
200 Oil cooler (heat exchanger)
210 Core part 211 Tube 220 Right header tank (header tank, one header tank)
230 Left header tank (header tank, other header tank)
240 Pipe 241 Curved part 250 Separator (partition part)
251 hole (opening)
261 Inlet pipe (inflow part)
262 Outlet pipe (outflow part)
311 dummy tube

Claims (7)

A plurality of stacked tubes (211) through which the fluid supplied from the piping circulates;
In the heat exchanger having a pair of header tanks (220, 230) connected to both longitudinal ends of the tube (211) and communicating with the tube (211),
A pipe having a channel cross-sectional area comparable to that of the pipe, disposed on one outer side in the stacking direction of the tubes (211), and communicating with the pair of header tanks (220, 230) ( 240)
Of the pair of header tanks (220, 230), the tank is provided at the boundary between the tube (211) and the pipe (240) in one header tank (220), and predetermined when the fluid passes through. A partition portion (250) having an opening (251) serving as a resistance of
Of the inflow part (261) into which the fluid flows in and the outflow part (262) out to the outside, the inflow part (261) is connected to the partition part (250) in the one header tank (220). On the other hand, the outflow portion (262) communicates with either the space on the tube (211) side or the space on the pipe (240) side on the opposite side,
Alternatively, the heat exchange is characterized in that the outflow part (262) communicates with either the space where the inflow part (261) is on the tube side or the other header tank (230), respectively. vessel.   The heat exchanger according to claim 1, wherein a curved portion (241) for absorbing thermal strain in a longitudinal direction is formed at an intermediate portion of the pipe (240). A heat exchanger (200) according to claim 1 or claim 2;
A plurality of other tubes (111) through which other fluids different from the fluid flow are stacked so that a pair of other header tanks (120, 130) communicate with both longitudinal ends of the other tubes (111). Another heat exchanger (100) connected to the
The other header tanks (120, 130) are connected to the header tanks (220, 230) so that the respective stacked states of the tubes (211) and the other tubes (111) are continuous, The dual heat exchanger, wherein the other heat exchanger (100) is integrally formed with the heat exchanger (200).   The duplex heat exchanger according to claim 3, wherein the tube (211) and the other tube (111) have the same specifications. The fluid and the other fluid have different temperatures,
Between the heat exchanger (200) and the other heat exchanger (100), a dummy tube (311) in which the flow of both the fluid and the other fluid is blocked is interposed. The dual heat exchanger according to claim 3 or 4.   The dual heat exchanger according to claim 5, wherein the tube (211), the other tube (111), and the dummy tube (311) have the same specifications. Arranged in the vehicle engine room,
The heat exchanger (200) is an oil cooler (200) that cools an ATF for a vehicle automatic transmission,
The dual heat according to any one of claims 3 to 6, wherein the other heat exchanger (100) is a refrigerant condenser (100) that condenses and liquefies the refrigerant of the vehicle refrigeration system. Exchanger.

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