JP5164885B2 - Combined heat exchanger - Google Patents

Description

  The present invention relates to a composite heat exchanger.

  Conventionally, the technology described in Patent Document 1 has been publicly known as a composite heat exchanger, and according to the present invention, the second heat exchanger is accommodated in the tank of the first heat exchanger.

US Pat. No. 6,755,158

However, the conventional invention has a problem that a temperature distribution is generated in the flow medium of the first heat exchanger after the heat exchange through the second heat exchanger.
Specifically, in the longitudinal direction of the second heat exchanger, the flow medium passing through the vicinity of the flow medium inlet of the tank of the first heat exchanger becomes the highest temperature, and the temperature decreases as the distance from the vicinity of the inlet increases. Little mixing occurs after passing through the heat exchanger.

  As a result, the temperature of the flow medium flowing for each tube of the first heat exchanger is different, and thermal stress due to the temperature distribution of the core portion of the first heat exchanger is generated, and the durability of the first heat exchanger is increased. There was a possibility that the property would decrease.

  The present invention has been made in order to solve the above-described problems, and an object of the present invention is to provide a composite heat exchanger that can suppress the generation of thermal stress due to the temperature distribution of the core portion of the first heat exchanger. Is to provide.

In the first aspect of the present invention, the first heat exchanger includes a pair of long tanks arranged at predetermined intervals, and a core composed of tubes and fins alternately stacked between the two tanks. And a housing part displaced outwardly from the at least one of the two tanks via a collecting part having a narrow passage, and a second heat exchanger is disposed in the housing part, and the housing A connection port that is an inlet / outlet of the distribution medium of the first heat exchanger is provided in the section, and the distribution amount of the distribution medium flowing in the tube corresponding to the predetermined divided body is regulated to be equal to or less than the distribution amount of the distribution medium flowing in the other tube. Adjusting means for performing heat exchange between the circulation medium of the first heat exchanger and the circulation medium of the second heat exchanger that circulates in the housing portion.

According to the first aspect of the present invention, an accommodation portion displaced outward from the one tank of the first heat exchanger via a collecting portion having a narrow passage is provided, and the second heat exchanger is disposed in the accommodation portion. ing.
Thereby, the temperature of the distribution medium flowing through the tube of the first heat exchanger can be made uniform, and the generation of thermal stress due to the temperature distribution of the core portion can be suppressed.

1 is a front view showing a composite heat exchanger of Example 1. FIG. FIG. 3 is an exploded perspective view illustrating a main part of the tank according to the first embodiment. It is a front view of the 2nd heat exchanger of Example 1. FIG. It is a perspective view of the 2nd heat exchanger of Example 1. FIG. FIG. 3 is a perspective view illustrating a main part of the tank according to the first embodiment. FIG. 3 is a front view illustrating a main part of the tank according to the first embodiment. It is a left view which shows the principal part of the tank of Example 1. It is a right view which shows the principal part of the tank of Example 1. It is a figure explaining before fixing (a) and after fixing (b) of the 2nd heat exchanger of Example 1. FIG. It is a figure explaining the inside of the tank of Example 1. FIG. It is a figure explaining (a) before fixation to the tube of the insertion member of Example 1, and (b) after fixation. It is a figure explaining the engine cooling circuit and supercharger circuit of Example 1. FIG. It is a figure explaining the effect | action of Example 1. FIG. It is a figure explaining the inside of the tank of Example 2. FIG. It is a perspective view explaining the deformation | transformation part of the tube of Example 2. FIG.

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

Example 1 will be described below.
The vehicle front-rear direction and the vehicle width direction will be described as the front-rear direction and the left-right direction.

First, the overall configuration will be described.
As shown in FIG. 1, the composite heat exchanger A1 of Example 1 includes a first heat exchanger 1, a second heat exchanger 2, and the like.

The first heat exchanger 1 is an intercooler incorporated in a supercharger circuit 23 to be described later, and includes a pair of long tanks 3 and 4 disposed at a predetermined interval on the left and right sides, and both of these tanks 3 , 4 is provided with a core portion 5 disposed between the two.
The core portion 5 is a plurality of flat tubular tubes 5a having both ends inserted and fixed to the tanks 3 and 4, and the tubes 5a are alternately stacked, and the corrugated top portion is joined to the adjacent tubes 5a. It is comprised from the plate-shaped fin 5b.
Note that the fin 5b may be omitted.
Further, a pair of reinforcements having both end portions inserted and fixed to both tanks 3 and 4 may be provided on both sides of the core portion 5 in the stacking direction to reinforce the connection.
Further, an inner fin may be provided inside the tube 5a.

As shown in FIG. 2, the tank 3 is comprised by the three division bodies 6-8 connected along the longitudinal direction.
The divided body 6 is formed in a bottomed cylindrical shape having a square cross section with the divided body 7 side as an opening side, and a tube hole 6a for inserting and fixing a corresponding end portion of the tube 5a on the inner side thereof. A plurality are formed at equal intervals (see FIG. 7).
The divided body 8 is formed in a bottomed cylindrical shape having a rectangular cross section with the divided body 7 side as an opening side, and a tube hole 8a for inserting and fixing a corresponding end portion of the tube 5a on the inner side thereof. A plurality are formed at equal intervals (see FIG. 7).

Inside the divided body 7, a plurality of tube holes 7a (five are shown in the first embodiment) for inserting and fixing corresponding ends of the tubes 5a are formed (see FIG. 7).
In addition, each divided body 6-8 is crimped in the state which overlapped on the tube plate made from aluminum with which a tube is inserted and fixed like a well-known intercooler, and this tube plate in the middle. You may comprise by the resin-made fixed and substantially vessel-shaped tank main body.

Openings 7b (the lower openings are not shown) are formed on the upper and lower surfaces of the divided bodies 7 to match the outer shapes of the end portions of the corresponding divided bodies 6 and 8, respectively.
In addition, the divided body 7 is formed with a storage portion 9 having a shape protruding rearward through a collecting portion 10 extending in the left-right direction.
A narrow passage 10a (see FIG. 9) is formed in the gathering portion 10, and a substantially rectangular protruding portion 11 that protrudes rearward in a state of communicating with the passage 10a is provided.
A circular opening 11 a and a plurality of bolt holes 11 b (three are shown in the first embodiment) are formed on the rear surface of the protrusion 11.
The opening 11a is formed to be somewhat larger than the opening diameter of the input port P3 described later.

The second heat exchanger 2 is accommodated in the protruding portion 11.
As shown in FIGS. 3 and 4, the second heat exchanger 2 is disposed between a pair of long tanks 13 and 14 disposed at a predetermined interval in the vertical direction, and both tanks 13 and 14. A core portion 15 is provided.
The core portion 15 is a plurality of flat tubular tubes 15a inserted into and fixed to the tanks 13 and 14, and laminated with the tubes 15a alternately, and corrugated fins having corrugated top portions joined to the adjacent tubes 15a. 15b.
Note that the fin 15b may be omitted.
In addition, a pair of reinforcements that are inserted into and fixed to the tanks 3 and 4 may be provided on both sides in the stacking direction of the core portion 15 to reinforce the connection.

Further, the inside of the tank 13 is divided into two chambers R1 and R3 by a partition wall 16, and an input port P1 is provided in communication with the chamber R1, while an output port P2 is provided in communication with the chamber R3. It has been.
On the other hand, a chamber R <b> 2 is provided inside the tank 14.
Further, both ports P1, P2 are provided in a state of penetrating through the flat closing member 17, and through holes 17a are formed at the four corners of the closing member 17, respectively.

Then, as shown in FIGS. 5 to 8, the corresponding end portions of both divided bodies 6 and 8 respectively corresponding to the openings 7 b on the upper and lower surfaces of the divided body 7 are inserted by a predetermined amount and joined. These three are connected.
Further, with the base portion 18 of the input port P3 shown in FIG. 2 in contact with the front surface of the protruding portion 11, the bolt B1 is screwed into the bolt hole 11b through the through hole 18a formed in the base portion 18. Thus, the input port P1 is provided so as to face the opening 11a.
Thereby, the input port P3 is fixed to the accommodating portion 9 so as to be detachable from the outside.
Note that a sealing member S1 (shown in bold lines) formed of a heat-resistant material in a sheet shape is attached to the back surface of the base portion 18 of the input port P3 to ensure the sealing performance in the housing portion 9. .

Further, as shown in FIG. 9, the second heat exchanger 2 is inserted obliquely into the opening 19 a of the inclined seat 19 formed on the upper surface of the protrusion 11, and the closing member 17 is inserted into the seat 19. The second heat exchanger 2 is inclined into the protruding portion 11 by screwing and fixing the bolt B2 from the through hole 17a of the closing member 17 to a bolt hole (not shown) of the seat portion 19 as being in contact. Arranged in a suspended state.
Thereby, the 2nd heat exchanger 2 is being fixed to the accommodating part 9 so that attachment or detachment is possible from the outside.
Note that a sealing member S2 (shown by a thick line) formed in a sheet shape with a heat-resistant material is attached to the back surface of the closing member 17 to ensure the sealing performance in the housing portion 9.
Further, the input port P3 and the core portion 1 5 as the core part 1 5 of the central axis X1 and the second heat exchanger 2 of the input port P3 is orthogonal is disposed.

  In the first embodiment, the input port P1 and the second heat exchanger 2 are arranged in an inclined shape, but this is not restrictive. Moreover, the 2nd heat exchanger 2 can also be fixed to the inner wall of the protrusion part 11 using the bracket which is not shown in figure.

A drain pipe 20 extending downward on the bottom of the protrusion 11 of the housing portion 9, specifically, the collecting portion 10 side of the second heat exchanger 2 in the protrusion 11 communicates with the protrusion 11 of the housing portion 9. Is provided.
Further, as shown in FIG. 1, a drain pipe 21 extending downward is provided at the bottom of the divided body 8 of the tank 3 so as to communicate with the tank 3.

The tank 4 is formed in a rectangular hollow body having a quadrangular cross section, and a corresponding end portion of the tube 5a is inserted and fixed therein.
An output port P4 that is bent rearward and protrudes obliquely upward is provided outside the tank 4 so as to communicate with the inside of the tank 4.

And as shown in FIG. 10, the fitting insertion member 30 is inserted and fixed to the edge part of the tube 5c inserted and fixed to the division body 7 among the some tubes 5a.
As shown in FIG. 11 (a), the entire insertion member 30 is formed in a substantially U shape, and protrudes outward from the base end portion of the insertion portions 30a, 30a facing each other in the U shape. Each of the locking portions 30b is formed.
And as shown in FIG.11 (b), by inserting the insertion parts 30a and 30a of the insertion member 30 in the tube 5c, and locking each latching | locking part 30b to the edge part of this tube 5c, The fitting member 30 is inserted and fixed in the tube 5c.
In addition, a gap O1 is formed between the end of the tube 5c and the fitting member 30.

In addition, all the constituent members of the composite heat exchanger A1 of Example 1 are all made of metal such as aluminum, and at least one of the joint portions of each constituent member is composed of a brazing sheet, Or the brazing material which apply | coated or stuck the flux previously is shape | molded.
And the 1st heat exchanger 1 will be joined to each other by heat-processing, after all the structural members except the 2nd heat exchanger 2 and the input port P3 are tentatively assembled beforehand. They are joined together and formed integrally.
On the other hand, the second heat exchanger 2 is also integrally formed by brazing and joining the joint portions of the constituent members by heat treatment after all the constituent members are preliminarily assembled.

Next, the engine cooling circuit 22 and the supercharger circuit 23 in which the composite heat exchanger A1 of Example 1 is employed will be described.
As shown in FIG. 12, in the engine cooling circuit 22, the engine A2, the radiator A3, the thermostat A4, and the water pump A5 are connected in a ring shape via passages a1 to a4 using cooling water as a circulation medium.
Further, a passage a5 that bypasses in parallel with the radiator A3 is provided.
The passage a6 branched from the passage a1 is connected to the input port P1 of the second heat exchanger 2 of the composite heat exchanger A1, while the passage a7 branched from the passage a2 is the output port of the second heat exchanger 2. Connected to P2.

The supercharger circuit 23 includes a composite heat exchanger A1, an engine A2, a supercharger A6, an EGR cooler A7, and the like using air as a circulation medium.
The upstream side of the compressor of the supercharger A6 is connected to the passage a8, while the downstream side is connected to the input port P3 of the first heat exchanger 1 of the composite heat exchanger A1 via the passage a9.
The output port P4 of the composite heat exchanger A1 is connected to an intake port (not shown) of the engine A2 via a passage a10 (intake manifold).
Further, an exhaust port (not shown) of the engine A2 is connected to the upstream side of the turbine of the supercharger A6 via a passage a11 (exhaust manifold).
Further, the downstream side of the turbine of the supercharger A6 is connected to the passage a12.
Further, the upstream side of the EGR cooler A7 is connected to the passage a11 via the passage a13, while the downstream side is connected to the passage a8 via the passage a14.
In addition, a check valve (not shown) is provided at an appropriate position such as the passage a5.

Next, the operation of the first embodiment will be described.
<Operation of engine cooling circuit and supercharger circuit>
In the composite heat exchanger A1 configured in this way, as shown in FIG. 12, in the engine cooling circuit 22, when the cooling water is below a predetermined temperature before the engine A2 is warmed up (at the time of low cooling water temperature) or the like. When the thermostat A4 closes the passage a2, the cooling water discharged from the engine A2 flows in the order of passage a1, passage a5, passage a3, water pump A5, passage a4, and returns to the engine A2.

When the cooling water exceeds a predetermined temperature after the engine A2 is warmed up (when the cooling water is hot) or the like, the thermostat A4 opens the passage a2, so that the cooling water discharged from the engine A2 is passed through the passage a1 → the radiator A3 → the passage a2. → Thermistor A4 → passage a3 → water pump A5 → passage a4 in this order and return to engine A2 again.
At this time, the high-temperature cooling water of around 80 ° C. (in the case of large vehicles) exchanges heat with the cooling air generated by the vehicle running wind or the fan 24 while passing through the radiator A3, and around 60 ° C. (in the case of large vehicles). Thus, the engine A2 can be cooled.

A part of the cooling water in the passage a1 first flows into the input port P1 of the second heat exchanger 2 through the passage a6.
Next, the cooling water that has flowed into the input port P1 of the second heat exchanger 2 flows into the chamber R1 of the tank 13, and then the chamber R2 of the tank 14 and the chamber R3 of the tank 13 through the corresponding tubes 15a, respectively. And then discharged from the output port P2 to the passage a7.

  In the supercharger circuit 23, the intake air sucked into the passage a8 through an air duct and a filter (not shown) is changed to a high temperature / high pressure state by the compressor of the supercharger A6, and then the first heat exchange is performed through the passage a9. Flows into the input port P3 of the device 1.

Next, the high-temperature intake air of about 170 ° C. (in the case of a large vehicle) that has flowed into the input port P3 of the first heat exchanger 1 flows into the housing portion 9, and passes through the core portion 15 of the second heat exchanger 2. After passing through and cooling with the cooling water flowing through the tube 15 a, it flows into the tank 3 through the collecting part 10.
Next, the intake air that has flowed into the tank 3 exchanges heat with the vehicle running wind that passes through the core portion 5 or the cooling air from the fan 24 while flowing into the tank 4 via each tube 5a, and is 40 ° C. Cooled back and forth (in the case of large vehicles).

  The intake air that has flowed into the tank 4 is discharged from the output port P4 to the passage a10 (intake manifold), and then flows into the intake port of the engine A2, thereby increasing the supercharging of the engine A2 and improving the engine output.

  The intake air introduced into the engine A2 becomes exhaust and drives the turbine of the supercharger A6 via the passage a11 (exhaust manifold), and then the exhaust purification catalyst, silencer, etc. (not shown) via the passage a12. It is discharged outside through the exhaust system.

  A part of the exhaust gas from the passage a11 (exhaust manifold) flows into the EGR cooler A7 through the passage a13, is cooled by exchanging heat with a distribution medium of a sub radiator (not shown), and then passed through the passage a14. Returned to the passage a8.

As described above, in the first embodiment, by introducing a part of the cooling water of the engine A2 into the second heat exchanger 2, the intake air of the first heat exchanger 1 is cooled before flowing into the core portion 5. Can remove rough heat.
As a result, by cooling the intake air stepwise by the first heat exchanger 1, it is possible to prevent thermal shock to each part due to a sudden temperature drop of the intake air, and at the same time assist cooling of the core portion 5. Efficient cooling.

Further, after a part of the exhaust gas is cooled by the EGR cooler A7, it is returned to the passage a8, whereby the unburned components contained in the exhaust gas can be introduced again into the engine A2 to purify the exhaust gas.
Further, in the first embodiment, since the exhaust gas discharged from the EGR cooler A7 is returned to the passage a8 before the compressor of the supercharger A6, the EGR rate is higher than when returning to the passage a10 (intake manifold). it can.

<Cooling of intake air by the second heat exchanger>
In the first embodiment, as described above, the input port P3 and the core portion 5 are arranged so that the central axis X1 of the input port P3 and the core portion 5 of the second heat exchanger 2 are orthogonal to each other.
As a result, as shown in FIG. 13, the intake air (shown by a broken line arrow in FIG. 13) that has flowed into the protruding portion 11 from the input port P <b> 3 easily passes through the core portion 5 of the second heat exchanger 2. (2) Hot air can be prevented from staying in the space on the input port P3 side of the heat exchanger 2, and the intake air can be cooled smoothly.

<Regarding the temperature uniformity of the intake air after passing through the second heat exchanger>
Here, in the conventional invention, a temperature distribution is generated in the flow medium of the first heat exchanger after the heat exchange through the second heat exchanger, and as a result, the temperature distribution of the core portion is caused. There is a possibility that the durability of the core portion is lowered due to the occurrence of thermal stress.

On the other hand, in the first embodiment, the housing portion 9 displaced outward from the tank 3 via the collecting portion 10 having the narrow passage 10a is provided, and the second heat exchanger 2 is disposed in the housing portion 9. ing.
As a result, the intake air that has passed through the second heat exchanger 2 can be mixed in the narrow passage 10 a of the collecting portion 10 from the housing portion 9 to make the temperature uniform, and then flow into the tank 3.
Therefore, the intake air having the same temperature can be caused to flow for each tube 5a, and the generation of thermal stress due to the temperature distribution of the core portion 5 can be prevented.

<About the circulation amount of the distribution medium flowing through each tube of the first heat exchanger>
In the first embodiment, as described with reference to FIGS. 10 and 11, the fitting member 30 is inserted and fixed to the end of the tube 5 c of the divided body 7.
In addition, a gap O1 is formed between the end of the tube 5c and the fitting member 30.
As a result, as shown in FIG. 10, most of the intake air (shown by broken line arrows in FIG. 10) that flows into the divided body 7 from the accommodating portion 9 through the collecting portion 10 is circulated in the longitudinal direction of the tank 3. Can flow into each tube 5a.
Further, a part of the intake air (indicated by a broken line arrow in FIG. 10) flowing into the tank 3 can be flowed into the tube 5c through the gap O1.

Accordingly, the amount of intake air flowing (inflow amount) in the tube 5c of the divided body 7 that is disposed near the inlet of the intake air to the tank 3 and that is easy for a large amount of intake air to flow in can be regulated by the insertion member 30.
That is, in the first embodiment, the clearance O1 is set so that the flow rate of the intake air flowing through the tube 5c is equal to or less than that of the other tubes 5a.

  As described above, in the first embodiment, the flow rate of the intake air in each tube 5a can be made uniform, and the temperature distribution of the core portion 5 can be made uniform.

In addition, you may provide the insertion member 30 in the edge part by the side of the tank 4 of the tube 5c.
Moreover, although the fitting member 30 was mounted | worn with all the tubes 5c in Example 1, it is not this limitation, The number of the tube 5c, the fitting member 30, etc. can be set suitably.
Furthermore, a so-called dead tube that completely eliminates the distribution of the distribution medium of the tube 5c may be employed.

<Thermal expansion / contraction of the second heat exchanger>
Since the cooling water flowing through the second heat exchanger 2 is the cooling water for the engine A2, it changes between the outside air temperature and around 80 ° C.
Accordingly, the second heat exchanger 2 is thermally expanded and contracted. Therefore, when the second heat exchanger 2 is fixed to the wall portion in the protruding portion 11 using a bracket or the like, the thermal expansion and contraction is performed. There is a risk of adverse effects of thermal stress that sometimes accompanies.

  On the other hand, in Example 1, the 2nd heat exchanger 2 is arrange | positioned in the state suspended in inclination in the protrusion part 11, and a clearance gap is formed between the wall parts in the protrusion part 11. FIG. Therefore, the second heat exchanger 2 can be fixed without being unnecessarily constrained, and can be thermally expanded and contracted mainly in the longitudinal direction of the tube 15a to prevent adverse effects due to thermal stress.

<About condensed water>
In the first embodiment, since the exhaust discharged from the EGR cooler A7 is returned to the passage a8 in front of the compressor 36a of the supercharger A6, the EGR rate can be increased, but the intake introduced into the first heat exchanger 1 is performed. The air contains moisture in the exhaust.
Since this moisture is acidic, there is a possibility of adversely affecting each part of the first heat exchanger 1 and the second heat exchanger 2.

On the other hand, in the first embodiment, as shown in FIG. 11, moisture contained in the intake air and moisture generated by cooling the intake air by the second heat exchanger 2 (illustrated by a two-dot chain line arrow in FIG. 11). ) Can be discharged downward from the bottom of the housing 9 through the drain pipe 20.
Therefore, the condensed water can be discharged at an early stage when the intake air flows into the first heat exchanger 1, and adverse effects of the condensed water on the first heat exchanger 1 and the second heat exchanger 2 can be prevented.
In addition, since the opening edge part of the division body 8 of Example 1 is connected in the state inserted in the bottom part of the division body 7, there exists a possibility that the condensed water collected on the bottom part of the accommodating part 9 may leak to the division body 8 side. Absent.

Further, as shown in FIG. 1, a drain pipe 21 extending downward is provided in communication with the divided body 7 at the bottom of the divided body 8, so that the condensed water accumulated in the tank 3 (FIG. 1 can be discharged to the outside through the drain pipe 21.
A hose (not shown) that extends to the bottom of the vehicle floor is attached to the lower ends of the drain pipes 20 and 21. The drain pipes 20 and 21 have a small diameter, but the drain pipes 20 and 21 can be provided with valves.

<Design flexibility of the first heat exchanger and the second heat exchanger>
In the first embodiment, the tank 3 is constituted by a plurality of divided bodies 6 to 8 connected along the longitudinal direction of the tank 3, and the divided body 7 is provided with a storage portion 9. Two heat exchangers 2 are disposed, and an input port P3 is provided in the accommodating portion 9.

Thereby, the division body 7 provided with the accommodating part 9 can be used as a common part, and the first heat exchanger 1 with various kinds of different heights of the core part 5 can be obtained by changing the design of only the other division body 7. Yes.
Or it can respond to the multiple types of 2nd heat exchanger 2 from which a size differs only by the design change of the division body 7 in which the accommodating part 9 was provided.

Further, since the input port P3 is fixed to the accommodating portion 9 so as to be removable from the outside, the angle, diameter, tip shape, etc. of the input port P3 can be easily changed.
The opening 11a of the protrusion 11 of the first embodiment is formed to be somewhat larger than the diameter of the input port P3, and the base 18 of the input port P3 is brought into contact with and communicated with the opening 11a. Therefore, it is possible to change the design for reducing the diameter and increasing the diameter by changing the design of only the input port P3.
Thus, in Example 1, the design freedom of the 1st heat exchanger 1 and the 2nd heat exchanger 2 can be expanded.

<About miniaturization of the first heat exchanger>
In the conventional invention, since it is necessary to store all the second heat exchangers in the tank of the first heat exchanger, a large space is required in the tank, and the tank is enlarged and wasteful.
Further, when the second heat exchanger is reduced in size, the height of the core portion is limited to be small, making practical adoption difficult.

On the other hand, in Example 1, since the 2nd heat exchanger is arrange | positioned in the accommodating part 9, a large space is not required in the tank 3, Especially the width direction dimension of the 1st heat exchanger 1 (tank 3). The degree of design freedom can be expanded.
Moreover, since the accommodating part 9 is made into the shape which protruded in the width direction from the tank 3 via the gathering part 10, the design freedom of the installation layout of a peripheral member can be expanded.

<Maintenance of the second heat exchanger>
The 2nd heat exchanger 2 is being fixed to the accommodating part 9 so that attachment or detachment is possible from the outside.
Therefore, at the time of replacement / repair / inspection of the second heat exchanger 2, the fastening of the bolt B2 can be released and the second heat exchanger 2 can be easily taken out from the accommodating portion 9, and the maintainability is excellent.

Next, the effect of Example 1 is described with (1)-(11) corresponding to Claims 1-4, 6-12.
(1) A pair of long tanks 3 and 4 in which the first heat exchanger 1 is arranged at a predetermined interval, and tubes 5a and fins arranged alternately between these tanks 3 and 4 A housing portion 9 having a core portion 5 made of 5b and displaced outward from the tank 3 via a collecting portion 10 having a narrow passage 10a is provided, and the second heat exchanger 2 is disposed in the housing portion 9 The input port P <b> 3 is provided in the storage unit 9, and heat is exchanged between the intake air of the first heat exchanger 1 that circulates in the storage unit 9 and the cooling water of the second heat exchanger 2.
As a result, the temperature of the intake air of the first heat exchanger 1 that exchanges heat with the second heat exchanger 2 is mixed and made uniform at the collecting portion 10, and then flows into each tube 5 a of the core portion 5. it can.
Accordingly, since the generation of thermal stress due to the heat distribution of the core portion 5 can be prevented, the cracks of the tubes 5a and 15a or the cracks of the tube holes 6a, 7a and 8a due to the thermal shock can be prevented. And, in turn, the durability of the first heat exchanger 1 can be improved.

(2) The tank 3 is composed of a plurality of divided bodies 6 to 8 connected along the longitudinal direction of the tank 3, and the aggregate portion 10 and the accommodating portion 9 are provided in the divided body 7.
Thereby, the design freedom of the 1st heat exchanger 1 and the 2nd heat exchanger 2 can be expanded.
For example, the divided body 7 provided with the accommodating portion 9 can be used as a common part, and the design of only the other divided body 7 can be changed to cope with various types of first heat exchangers 1 having different height dimensions of the core portion 5. it can.
Or it can respond to the multiple types of 2nd heat exchanger 2 from which a size differs only by the design change of the division body 7 in which the accommodating part 9 was provided.

(3) An adjusting means (insertion member 30) is provided that regulates the flow rate of the intake air flowing through the tube 5c corresponding to the divided body 7 to be equal to or less than the flow rate of the intake air flowing through the other tube 5a.
Thereby, it can avoid that the distribution | circulation amount of the intake air which flows into the tube 5c increases compared with the other tubes 5a, and can make temperature distribution of the core part 5 uniform.

(4) The adjusting means is the fitting member 30 inserted and fixed to the end of the tube 5c.
Thereby, the effect | action and effect similar to (3) can be acquired.

(5) The input port P3 is fixed to the accommodating portion 9 so as to be removable from the outside.
Thereby, it can respond easily to input ports P3, such as various angles and diameters.

(6) The 2nd heat exchanger 2 was fixed to the accommodating part 9 so that attachment or detachment was possible from the outside.
Thereby, the maintainability of the 2nd heat exchanger 2 can be improved.

(7) The second heat exchanger 2 includes a pair of long tanks 13 and 14 arranged at a predetermined interval, and tubes 15a and fins alternately arranged between the tanks 13 and 14. The connection port P3 and the core portion 15 are arranged so that the core portion 15 including 15b is provided and the central axis X1 of the connection port P3 and the core portion 15 of the second heat exchanger 2 are orthogonal to each other.
Thereby, the heat exchange with the 1st heat exchanger 1 and the 2nd heat exchanger 2 can be performed efficiently.

(8) The input port P3 is used as the inlet of the intake air of the first heat exchanger 1, and the first heat exchanger is exchanged by heat exchange between the intake air of the first heat exchanger 1 and the cooling water of the second heat exchanger 2. 1 intake air was cooled.
Thereby, the intake air of the 1st heat exchanger 1 can be cooled in steps, the generation | occurrence | production of the thermal shock resulting from the rapid temperature fall of intake air can be avoided, and the cooling performance of the 1st heat exchanger 1 is improved. it can.

(9) The first heat exchanger 1 is an intercooler, and the flow medium of the second heat exchanger 2 is cooling water for the engine cooling circuit 22.
Accordingly, the present invention is suitable for application to an intercooler in which the demand for cooling specifications is increasing with the recent increase in output of the engine A2.
In addition, it is possible to realize a combination of distribution media having an optimum temperature relationship as a heat exchange medium.

(10) A drainage pipe 20 capable of draining condensed water is provided at the bottom of the housing 9.
Thereby, the bad influence to the 1st heat exchanger 1 and the 2nd heat exchanger 2 by condensed water can be prevented.

(11) A drain pipe 21 capable of draining condensed water is provided at the bottom of the tank 3.
Thereby, the bad influence to the 1st heat exchanger 1 and the 2nd heat exchanger 2 by condensed water can be suppressed to the minimum.

Example 2 will be described below.
Note that in the second embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, description thereof is omitted, and only differences are described in detail.

As shown in FIGS. 14 and 15, in the second embodiment, instead of the fitting member 30 described in the first embodiment, a deformed portion 31 in which the end of the tube 5 c is reduced in diameter is employed.
Further, an opening O2 serving as a substitute for the gap O1 described in the first embodiment is formed at the end of the deformable portion 31.
Therefore, in Example 2, it can prevent that the distribution | circulation amount of the intake air which flows into the tube 5c of the division body 7 increases compared with the other tube 5a, and the effect | action and effect similar to Example 1 are acquired.
Further, the deformed portion 31 can be formed by a simple operation of deforming the end portion of the tube 5c with a jig or the like to reduce the diameter, and the number of parts does not increase.
A so-called dead tube in which the deformed portion 31 is completely crushed and the opening O2 is eliminated may be employed.

Next, the effect of Example 2 will be described together with (12) corresponding to claim 5.
(12) The adjusting means is the deformed portion 31 in which the end portion of the tube 5c corresponding to the divided body 7 is reduced in diameter.
Thereby, the effect | action and effect similar to (3) and (4) can be acquired.

Although the embodiments have been described above, the present invention is not limited to the above-described embodiments, and design changes and the like within the scope not departing from the gist of the present invention are included in the present invention.
For example, the first heat exchanger 1 may be a radiator and the second heat exchanger 2 may be an oil cooler, and the present invention may be applied to a so-called radiator with a built-in oil cooler.
In this case, the input port P3 is used as the outlet of the flow medium of the first heat exchanger 1 (radiator) and the flow of the first heat exchanger 1 (radiator) is the same as that described in the known Japanese Patent Application Laid-Open No. 2008-32242. The flow medium of the second heat exchanger 2 (oil cooler) is cooled by heat exchange between the medium (cooling water) and the flow medium (oil) of the second heat exchanger 2 (oil cooler). 13 and 14).

The material of each constituent member can be set as appropriate, and the fixing method can be changed according to the material.
Moreover, the division number of the division body of the tank 3, a connection structure, etc. can be set suitably.
For example, the divided bodies may be fixed using bolts or the like.
Further, a part of the tank 3 may be made of resin.

Furthermore, in the embodiment, the accommodating portion 9 that protrudes rearward from the divided body 7 via the collecting portion 10 extending in the left-right direction is employed, but the direction of displacement of the collecting portion 10 and the accommodating portion 9 is appropriately set. it can.
It is also conceivable to form the divided bodies 6 to 8 integrally.

A1 Combined heat exchanger A2 Engine A3 Radiator A4 Thermostat A5 Water pump A6 Supercharger A7 EGR cooler a1, a2, a3, a4, a5, a6, a7, a8, a9, a10, a11, a12, a13 passage B1, B2 Bolt O1 Clearance O2 Opening P1, P3 Input port P2, P4 Output port R1, R2, R3 Chamber S1, S2 Seal member 1 First heat exchanger 2 Second heat exchanger 3, 4, 13, 14 Tank 5, 15 Core parts 5a, 5c, 15a Tubes 5b, 15b Fins 6, 7, 8 Divided bodies 6a, 7a, 8a Tube hole 7b Opening 9 Housing 10 Collecting part 10a Passage 11 Projection 11a Opening 11b Bolt hole 16 Partition wall 17 closing member 17a through-hole 18 base 18a through-hole 19 seat 19a opening 20, 21 drain pipe 22 engine Cooling circuit 23 supercharger circuit 24 fan 30 fitted insertion member 30a inserted portion 30b engaging portion 31 deformed portions

Claims (13)

The first heat exchanger includes a pair of long tanks arranged at a predetermined interval, and a core part composed of tubes and fins alternately stacked between the two tanks,
While providing a storage part displaced outwardly from a collecting part having a narrow passage from at least one of the two tanks, a second heat exchanger is disposed in the storage part,
A connection port that is an entrance / exit of the flow medium of the first heat exchanger is provided in the housing portion,
Adjusting means for regulating the flow rate of the flow medium flowing in the tube corresponding to the predetermined divided body to be equal to or lower than the flow rate of the flow medium flowing in the other tube;
A composite heat exchanger characterized in that heat is exchanged between the flow medium of the first heat exchanger and the flow medium of the second heat exchanger that circulate in the housing portion. The composite heat exchanger according to claim 1, wherein
The one tank is composed of a plurality of divided bodies connected along the longitudinal direction of the tank,
A composite heat exchanger, wherein the collecting section and the housing section are provided in a predetermined divided body among the plurality of divided bodies. The composite heat exchanger according to claim 1 or 2,
The composite heat exchanger according to claim 1, wherein the adjusting means is a fitting member inserted and fixed to an end portion of a tube corresponding to the predetermined divided body . The composite heat exchanger according to claim 1 or 2 ,
The composite heat exchanger according to claim 1, wherein the adjusting means is a deformed portion obtained by reducing the diameter of an end portion of a tube corresponding to the predetermined divided body. In the composite heat exchanger according to any one of claims 1 to 4 ,
The composite heat exchanger, wherein the connection port is fixed to the housing part so as to be removable from the outside . In the composite heat exchanger according to any one of claims 1 to 5,
The composite heat exchanger, wherein the second heat exchanger is fixed to the housing part so as to be removable from the outside . In the composite heat exchanger according to any one of claims 1 to 6,
The second heat exchanger includes a pair of long tanks arranged at a predetermined interval, and a core part composed of tubes and fins alternately stacked between the two tanks,
The composite heat exchanger , wherein the connection port and the core portion are arranged so that a central axis of the connection port and a core portion of the second heat exchanger are orthogonal to each other . In the composite heat exchanger according to any one of claims 1 to 7,
The connection port as an inlet of a flow medium of the first heat exchanger;
A composite heat exchanger, wherein the flow medium of the first heat exchanger is cooled by heat exchange between the flow medium of the first heat exchanger and the flow medium of the second heat exchanger . The composite heat exchanger according to claim 8 ,
The first heat exchanger is an intercooler,
A composite heat exchanger characterized in that the circulation medium of the second heat exchanger is cooling water of an engine cooling circuit . The composite heat exchanger according to claim 9, wherein
A composite heat exchanger characterized in that a first drainage part capable of draining condensed water is provided at the bottom of the housing part . The composite heat exchanger according to claim 9 or 10,
A composite heat exchanger characterized in that a second drainage unit capable of draining condensed water is provided at the bottom of the one tank . In the composite heat exchanger according to any one of claims 1 to 7 ,
The connection port as an outlet of the flow medium of the first heat exchanger;
A composite heat exchanger, wherein the flow medium of the second heat exchanger is cooled by heat exchange between the flow medium of the first heat exchanger and the flow medium of the second heat exchanger . The composite heat exchanger according to claim 12 ,
The first heat exchanger is a radiator,
A composite heat exchanger, wherein the second heat exchanger is an oil cooler .

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