WO2008072730A1

WO2008072730A1 - Compound heat exchanger and heat exchanger

Info

Publication number: WO2008072730A1
Application number: PCT/JP2007/074127
Authority: WO
Inventors: Hiroki Yoshioka; Yuichi Meguriya
Original assignee: Calsonic Kansei Corporation
Priority date: 2006-12-14
Filing date: 2007-12-14
Publication date: 2008-06-19

Abstract

A refrigerant cooling section (8) of a compound heat exchanger (1) has a core constructed by multiply stacking flat refrigerant tubes (10) and also has refrigerant tanks (20A, 20B) communicating with the flat refrigerant tubes (10) on both sides in the longitudinal direction of the flat refrigerant tubes (10). In the lateral direction of the flat refrigerant tubes (10) of the refrigerant tanks (20A, 20B), the width (L1) of in-tank passages (26) is less than the width (L2) of the flat refrigerant tubes.

Description

Specification

Combined heat exchanger and heat exchanger

Technical field

[0001] The present invention relates to a composite heat exchanger and a heat exchanger.

Background art

For example, Japanese Patent Application Laid-Open No. 2006-162176 discloses a heat exchanger that dissipates heat of engine cooling water. This heat exchanger is a cooling system in which a plurality of cooling water flat tubes for exchanging heat between engine cooling water and air and the opening end of one end in the longitudinal direction of the plurality of cooling water flat tubes are connected. A water tank and a cooling water tank to which open ends at the other ends in the longitudinal direction of the plurality of cooling water flat tubes are connected in communication are configured. The engine cooling water that has become hot due to heat drawn from the engine flows into the heat exchanger and flows in the order of the upstream cooling water tank, the cooling water flat tube, and the downstream cooling water tank. And go back.

[0003] A coolant cooling unit is disposed in a cooling water tank on the downstream side of the heat exchanger. The refrigerant water cooling unit circulates the refrigerant discharged from the compressor of the refrigeration cycle and cools the refrigerant with the cooling water in the cooling water tank.

[0004] This refrigerant water cooling section is configured to include a refrigerant flat tube, a refrigerant tank into which refrigerant from the compressor flows in, and a refrigerant tank into which refrigerant flowing through the refrigerant flat tube flows.

Disclosure of the invention

However, since the high-temperature and high-pressure refrigerant flows into the refrigerant tank of the refrigerant water cooling section from the compressor side, it is necessary to ensure the strength of the refrigerant tank. If it is attempted to obtain sufficient strength of the refrigerant tank in the refrigerant water cooling section, the refrigerant tank may be increased in size. If the refrigerant tank becomes large in this way, there is a problem that the layout becomes difficult.

[0006] Further, in a heat exchanger configured to include a tube and a pair of tanks at both ends in the longitudinal direction of the tube, when the tank is enlarged, the longitudinal size of the tube is reduced and the heat exchange performance is degraded. . [0007] A first object of the present invention is to reduce the size of the refrigerant tank while ensuring the strength of the refrigerant tank in the refrigerant water cooling section.

[0008] A second object of the present invention is to reduce the size of the refrigerant water cooling unit while ensuring the strength of the refrigerant water cooling unit.

[0009] A third object of the present invention is to improve heat exchange efficiency by increasing the longitudinal size of a tube in a heat exchanger including a tube and a pair of tanks.

[0010] In the first aspect of the present invention, a core portion in which a plurality of cooling water flat tubes (5a) each having an internal passage for cooling water are stacked in multiple stages, and the cooling water that has passed through the core portion is provided. A cooling water heat exchanger (5) having an inflowing cooling water tank (5c), and the cooling water tank (5c) of the cooling water heat exchanger (5), in which refrigerant is contained. A combined heat exchanger (1) having a refrigerant water cooling section (8) for exchanging heat between the cooling medium and the cooling water in the cooling water tank (5c) by circulating the refrigerant; The water cooling section (8) extends in the stacking direction of the core section in which a plurality of refrigerant flat tubes (10) each having an internal refrigerant path are stacked in multiple stages and the refrigerant flat tubes (10). A tank internal passage (26) that is inserted into one end of the refrigerant flat tube (10) in the longitudinal direction. A first refrigerant tank (20A) communicating with the passage, and a tank passage (26) extending in the stacking direction of the refrigerant flat tube (10), and the refrigerant flat tube (10) A second refrigerant tank (20B) in which the other opening end in the longitudinal direction is inserted and communicated with the internal passage,

The first refrigerant tank (20A) and the second refrigerant tank (20B) have a width (L1) of the tank passage (26) along the width direction of the refrigerant flat tube (10). Smaller than the width (L2) of the flat tube for cooling medium!

[0011] A second aspect of the present invention is a first heat exchanger (5) that dissipates the heat of the first heating element via the first fluid, in which the first fluid flows. A first heat exchanger (5) having one fluid tank (5c), a second heat exchanger (7) for radiating the heat of the second heating element via the second fluid, and the second heat exchanger (5). A part of the second fluid line that circulates the second fluid is connected to the heating element and the second heat exchanger (7), and is built in the first fluid tank (5c). , A second fluid cooling unit that performs heat exchange between the first fluid and the second fluid in the first fluid tank (5c). A combined heat exchanger (1) having a rejection section (8), wherein the second fluid cooling section (8) includes a plurality of flat tubes (10) each having a second fluid internal passage. And a tank internal passage (26) extending in the laminating direction of the flat tube (10), and one open end of the flat tube (10) is inserted into the first passage. 2 Communicating with the fluid internal passage and extending in the stacking direction of the upstream second fluid tank (20A) to be supplied to each of the flat tubes (10) and the flat tubes (10) The tank has a passage (26) inside, the other open end of the flat tube (10) is inserted and communicates with the second fluid internal passage, and flows through the flat tube (10). A second fluid tank (20B) on the downstream side into which the second fluid flows, and the second fluid tank (20A) on the upstream side and the lower fluid tank (20A) The second fluid tank side (20B) is smaller than the tank passage width (L1) is earlier SL flat tubes (26) Width (L2)! /,.

[0012] A third aspect of the present invention provides a first heat exchange in which heat of the first heating element is radiated through the first fluid by circulating a first fluid between the first heating element and the first heating element. Circulating a second fluid between a first heat exchanger (5) having a first fluid tank (5c) through which the first fluid flows and a second heating element The second heat exchanger (7) for radiating the heat of the second heating element via the second fluid is connected to the second heating element and the second heat exchanger (7). The second fluid line that circulates the second fluid constitutes a part of the second fluid line, and is attached to the first fluid tank (5c) and connected to the first fluid tank (5c). A composite heat exchanger having a first fluid from a first fluid tank (5c) and a second fluid cooling section (70) for exchanging heat between the second fluid and the second fluid The cooling unit (70) includes the first fluid The first plate and the second plate are formed by alternately laminating the plate-shaped first plate and the second plate (76, 77) whose plate surface is perpendicular to the flow direction of the first fluid from the tank (5c). Are separated from each other and the peripheral edge thereof is liquid-tightly joined. The first passage (78) through which the second fluid flows and the second passage through which the first fluid flows are arranged in the stacking direction of the plates. (79) and are alternately provided.

[0013] In a fourth aspect of the present invention, there is provided a core portion in which a plurality of cooling water flat tubes (5a) each having an internal passage for cooling water are stacked in a plurality of stages, and cooling water having passed through the core portion. A cooling water heat exchanger (5) having an inflowing cooling water tank (5c), and the cooling water heat exchange Refrigerant water cooling unit (5) which is built in the cooling water tank (5c) of the cooler (5) and exchanges heat between the cooling medium and the cooling water in the cooling water tank (5c) by circulating the refrigerant therein. 8), wherein the refrigerant water cooling section (8) has a plurality of refrigerant flat tubes (10) each having a refrigerant internal passage laminated in a plurality of stages. The tank has a tank passage (26) extending in the stacking direction of the refrigerant flat tube (10), and one open end of the refrigerant flat tube (10) in the longitudinal direction is inserted. A first refrigerant tank (20A) communicating with the refrigerant internal passage and a tank internal passage (26) extending in the stacking direction of the refrigerant flat tube (10) and A second refrigerant tank (20B) in which the other opening end in the longitudinal direction of the flat tube (10) is inserted and communicated with the internal passage; And the tank member constituting the refrigerant tank (20A, 20B) is disposed on the outer side in the longitudinal direction of the tube (10) from the longitudinal end face (1 la) of the plurality of flat tubes for refrigerant (10). An outer tank member (21), the inner surface of the outer tank member (21) being the outer surface of the tank passage (26), and the tube (10) from the longitudinal end surface (11a) of the tube (10). ) Inside the tank in the longitudinal direction.

[0014] A fifth aspect of the present invention includes a plurality of tubes (10) each having an in-tube flow passage (13) therein, and disposed on both ends in the longitudinal direction of the tubes (10). A heat exchanger (8) comprising a pair of tanks (20A, 20B) having a tank internal passage (26) connected to the internal flow passage (13), the tank (20A, 20B) The tank member constituting the outer tank member has an outer tank member (21) disposed on the outer side in the longitudinal direction of the tube (10) with respect to the longitudinal end surface (11a) of the plurality of tubes (10). The inner surface of the tank (21) is the outer surface of the tank passage (26), and the tank passage (26) is formed on the inner side in the longitudinal direction of the tube (10) from the longitudinal end surface (1 la) of the tube (10). It has been done.

Brief Description of Drawings

FIG. 1 is a block diagram conceptually showing a composite heat exchanger 1 for a vehicle according to a first embodiment of the present invention.

FIG. 2 is a perspective view of the composite heat exchanger 1 for the vehicle.

[Fig. 3] Fig. 3 is a front view of the sub radiator 5 of the composite heat exchanger 1 for the vehicle. [FIG. 4] FIG. 4 is a front view of the cooling water cooling unit 8 disposed in the tank 5c of the sub-rajator 5.

FIG. 5 is a side view of the refrigerant water cooling unit 8.

6] FIG. 6 is an exploded perspective view of the upper part of the refrigerant water cooling unit 8.

7] Fig. 7 is an exploded perspective view of the sub radiator 5.

8] FIG. 8 is a front view of the refrigerant water cooling unit 8 of the second embodiment.

FIG. 9 is a side view of the refrigerant water cooling unit 8.

FIG. 10] FIG. 10 is a perspective view of the vehicle composite heat exchanger 1 of the third embodiment.

FIG. 11 is a front view of the sub radiator 5 and the coolant cooling unit 70 of the composite heat exchanger 1 for the vehicle.

[FIG. 12] FIG. 12 is a side view schematically showing shell plates 76 and 77 constituting the refrigerant water cooling unit 70, (a) showing the first shell plate 76, and (b) showing the second shell plate 76. Showing shell plate

Yes

FIG. 13 is a cross-sectional view of the coolant cooling unit 70 along the AA cross section of FIG.

14] FIG. 14 is a block diagram conceptually showing the combined vehicle heat exchanger 1 of the fourth embodiment.

FIG. 15 is a perspective view of the composite heat exchanger 1 for a vehicle.

16] FIG. 16 is a front view of the refrigerant water cooling section 8 installed in the tank section 5c of the sub radiator 5 of the composite heat exchanger 1 for the vehicle.

17] Fig. 17 is a side view of the refrigerant water cooling unit 8.

18] FIG. 18 is an exploded perspective view of the main part of the refrigerant water cooling unit 8.

[FIG. 19] FIG. 19 (a) is a cross-sectional view of the main part showing the arrangement of the inner fins in the tube of the cooling water cooling unit 8, and FIG. 19 (b) is a front view of the main part of the inner fin.

[FIG. 20] FIG. 20 shows a modification of the fourth embodiment. FIG. 20 (a) is a cross-sectional view of the main part showing the arrangement of the inner fin in the tube, and FIG. 20 (b) is a main part of the inner fin. FIG. 21 is a front view of the refrigerant water cooling unit 8 of the fifth embodiment.

22] FIG. 22 is a side view of the refrigerant water cooling unit 8.

Fig. 23] Fig. 23 is an exploded perspective view of the main part of the refrigerant water cooling unit 8.

[FIG. 24] FIG. 24 is a cross-sectional view taken along line AA in FIG. [FIG. 25] FIG. 25 is a BB cross-sectional view in FIG.

BEST MODE FOR CARRYING OUT THE INVENTION

[0016] (First embodiment)

The first embodiment will be described with reference to FIGS. The vehicle composite heat exchanger 1 according to the present embodiment is applied to a hybrid vehicle that can run on one or both of the driving force of an engine and the driving force of an electric motor. It is arranged in a cooling air duct that takes the traveling air (cooling air) into the gin room.

FIG. 1 is a block diagram conceptually showing a composite heat exchanger 1 for a vehicle according to this embodiment.

As shown in FIG. 1, the vehicular combined heat exchanger 1 includes a main radiator 3 that cools the engine 2 of the vehicle, and an electric drive unit that assists the engine 2 (in this embodiment, the electric motor and its control). Electric drive unit including electronic parts for the vehicle) 4 Sub radiator 5 (first heat exchanger) that cools the cooling medium that circulates the refrigeration cycle of the air conditioning system for cooling the passenger compartment (for example, CFC-12) Etc.) and a condenser 6 for cooling. The capacitor 6 is cooled by the refrigerant water cooling unit 8 that primarily cools the high-temperature and high-pressure refrigerant discharged from the compressor of the refrigeration cycle, and the refrigerant water cooling unit 8 downstream of the refrigerant water cooling unit 8. And a refrigerant air cooling unit (second heat exchanger) 7 for secondary cooling of the generated refrigerant.

[0018] As shown in FIG. 2, on the windward side of the main radiator 3 for cooling the engine, a sub radiator 5 and a refrigerant air cooling unit 7 for the condenser 6 are arranged facing the main radiator 3. . The sub radiator 5 and the refrigerant air cooling part 7 of the condenser 6 are arranged vertically, the sub radiator 5 is arranged opposite to the upper half of the main radiator 3, and the air cooling part 7 of the condenser 6 faces the lower half of the main radiator 3. Has been placed. The refrigerant water cooling unit 8 of the capacitor 6 is built in the sub-rajator 5.

[0019] The refrigerant water cooling unit 8 of the capacitor 6 can be rephrased as a water cooling type capacitor, and the refrigerant air cooling unit 7 of the capacitor 6 can be rephrased as an air cooling type capacitor.

[0020] Referring to FIG. 1, in the cooling water line through which the cooling water C3 circulates, the circulation pump P3 for circulating the cooling water C3 to the cooling water line, the engine 2, and the heat of the engine 2 to the atmosphere. Release Heated main radiator 3 is interposed. When the circulation pump P3 is driven, the cooling water (C3in) from the engine 2 is supplied to the main radiator 3 and heat exchange is performed between the main radiator 3 and air. Then, the cooling water (C3 out) from the main radiator 3 is supplied to the engine 2 again.

[0021] In addition, the cooling water line through which the cooling water C1 circulates dissipates heat from the circulation pump P1 for circulating the cooling water C1 through the cooling line, the electric drive unit 4, and the electric drive unit 4 to the atmosphere. Subjector 5 is installed. When the circulation pump P1 is driven, the cooling water (Clin) from the electric drive unit 4 is supplied to the sub radiator 5 and heat exchange is performed between the sub radiator 5 and the air. Then, the cooling water (Clout) from the sub radiator 5 is supplied to the electric drive unit 4 again.

[0022] The air conditioning system for cooling the passenger compartment has an refrigeration cycle evaporator arranged in the passenger compartment to cool the air in the passenger compartment, and a condenser 6 in the refrigeration cycle is arranged outside the passenger compartment to absorb heat by the evaporator. Thus, the heat in the passenger compartment is dissipated outside the passenger compartment. The refrigeration cycle includes a compressor that circulates refrigerant in the refrigeration cycle, a condenser 6, a liquid tank, expansion means, and an evaporator connected in this order. The high-temperature and high-pressure gas refrigerant (C2in) compressed by the compressor is supplied to the refrigerant water cooling unit 8 of the capacitor 6 and then supplied to the refrigerant air cooling unit 7 of the capacitor. Heat is exchanged between the refrigerant water cooling unit 8 and the refrigerant air cooling unit 7, and the gas refrigerant becomes a high-pressure liquid refrigerant or a gas-liquid mixed refrigerant. The refrigerant (C2out) from the refrigerant air cooling unit 7 is gas-liquid separated in the liquid tank, and then adiabatically expanded by an expansion means to form a low-temperature low-pressure liquid refrigerant or gas-liquid mixed refrigerant. After replacing it into a low-pressure gas refrigerant, it is returned to the compressor.

FIG. 3 is a front view schematically showing the structure of the sub radiator 5. The sub radiator 5 is configured to include a core portion formed by alternately laminating heat radiation fins 5b and cooling water flat tubes 5a, and a pair of cooling water tanks 5c.

The radiating fin 5b is a thin plate-like member having substantially the same width as the width L4 of a cooling water flat tube 5a described later, and its front view shape is corrugated as shown in FIG. . In addition, the cooling water flat tube 5a is a thin tube having a flat cross-sectional shape. It is a long plate-like member, and is formed from, for example, an aluminum alloy. In the cooling water flat tube 5a, a plurality of passages penetrating the inside thereof are formed along the longitudinal direction, and the cooling water flows through the respective passages. The core portion is configured by alternately stacking the cooling fins 5b and the cooling water flat tubes 5a by sandwiching the cooling water flat tubes 5a from both sides by a pair of heat dissipating fins 5b. Reinforces 5d are installed on the outer sides of the outermost (upper and lower) radiating fins 5b, respectively, and a proper amount of load is applied to the core portion in the stacking direction by a pair of reinforcements 5d. Is sandwiched between. Each of the flat tubes 5a for cooling water constituting the core portion has one opening end portion in the longitudinal direction inserted into the cooling water tank 5c on the upstream side, and the other opening end portion in the longitudinal direction on the downstream side. Inserted into tank 5c. Thereby, the internal space of each cooling water tank 5c communicates with the internal passage of the cooling water flat tube 5a. The upstream cooling water tank 5c is connected to the connector 54 that constitutes the cooling water inlet of the sub radiator 5. The downstream cooling water tank 5c is connected to the connector that constitutes the cooling water outlet of the sub radiator 5. 53 is connected! /

[0025] As shown in Fig. 2, the refrigerant air cooling unit 7 has the same basic configuration as that of the sub radiator 5, and is configured by alternately stacking radiating fins 7b and refrigerant flat tubes 7c. And a pair of refrigerant tanks 7c. The main radiator 3 has basically the same configuration, and includes a core portion configured by alternately stacking heat radiation fins and flat tubes for cooling water, and a pair of cooling water tanks 3c.

FIG. 4 is a front view schematically showing the configuration of the refrigerant water cooling unit 8, and FIG. 5 is a side view schematically showing the configuration of the refrigerant water cooling unit 8. FIG. 6 is an exploded perspective view schematically showing the configuration of the upper side of the refrigerant water cooling unit 8.

[0027] The refrigerant water cooling section 8 (water cooling condenser) constitutes a part of the refrigerant line from the compressor to the refrigerant air cooling section 7 (air cooling condenser). This refrigerant water cooling section 8 is built in the cooling water tank 5c on the downstream side of the scrambler 5, and performs heat exchange between the cooling water in the cooling water tank 5c and the refrigerant in the refrigeration cycle. As a premise that the refrigerant flows into the refrigerant air cooling section 7 of the condenser 6, the refrigerant is primarily cooled.

[0028] Specifically, the refrigerant water cooling unit 8 includes an upper refrigerant tank 20A (first cooling unit) on the refrigerant inlet side. Medium tank), the lower refrigerant tank 20B (second refrigerant tank) on the refrigerant outlet side, and both refrigerant tanks 20A and 20B are connected to each other to exchange heat between the refrigerant and the cooling water. And a refrigerant flat tube 10 (core part) for performing!

[0029] The refrigerant tank 20A on the refrigerant inlet side of the refrigerant water cooling section 8 is joined inside the cooling water tank 5c in contact with the upper wall (one longitudinal end) of the cooling water tank 5c. A connector 24 that penetrates the upper wall of 5c and protrudes into the cooling water tank 5c is connected in communication. This connector 24 constitutes the inlet of the refrigerant water cooling unit 8 and is connected to a refrigerant pipe from the compressor.

[0030] On the other hand, the refrigerant tank 20B on the refrigerant outlet side of the refrigerant water cooling section 8 is brazed while being in contact with the lower wall (the other end in the longitudinal direction) of the cooling water tank 5c inside the cooling water tank 5c. Thus, a connector 25 that penetrates the lower wall of the cooling water tank 5c and protrudes into the cooling water tank 5c is connected in communication. The connector 25 constitutes an outlet of the refrigerant water cooling unit 8 and is connected to a refrigerant pipe to the refrigerant air cooling unit 7 of the capacitor 6.

[0031] The refrigerant tank 20A on the refrigerant inlet side includes a pipe portion formed by combining the first tank plate 22 and the second tank plate 21, and a pair of closing plates that close the openings at both ends of the pipe portion. And 23. The refrigerant tank 20A on the refrigerant inlet side distributes and supplies the refrigerant from the compressor to each refrigerant flat tube 10 (core part) via a tank passage 26 formed inside.

The first tank plate 22 is a flat plate having a substantially rectangular shape, and is disposed on the lower surface of the second tank plate 21. The first tank plate 22 has a slit-like tube insertion hole 22c extending in the flow direction of the cooling water in the cooling water tank 5c. A plurality of the tube insertion holes 22c are formed at a predetermined interval in a direction orthogonal to the flow direction of the cooling water. The shape of each tube insertion hole 22c corresponds to the outer shape of the refrigerant flat tube 10 in the core portion described later, and the refrigerant flat tube 10 is fitted therein. That is, the number of tube insertion holes 22c formed in the first tank plate 22 corresponds to the number of the refrigerant flat tubes 10.

In the present embodiment, in the stacking direction of the refrigerant flat tubes 10, the width L3 of the core portion of the refrigerant water cooling portion is the width of the core portion in the sub radiator 5 (specifically, the cooling water flatness). The number of the refrigerant flat tubes 10 is set so as to be equal to or less than the width L4 of the tube 5a.

The second tank plate 21 is a plate-like member having a substantially rectangular shape corresponding to the outer peripheral shape of the first tank plate 22. The second tank plate 21 has a bent portion that is curved in a convex shape toward the outside in the longitudinal direction (connector 24 side) of the cooling medium flat tube 10 in the central region. By this bent portion, a space in which the outline of the cross-sectional shape has an arc shape is formed in the second tank plate 21. This space extends in the stacking direction of the refrigerant flat tubes 10 and functions as an in-tank passage 26 for supplying the refrigerant to the core portion. As shown in FIG. 4, in the short side direction of the refrigerant flat tube 10 (in other words, the flow direction of the cooling water C1), the width L1 of the tank passage 26 is larger than the width L2 of the refrigerant flat tube 10. It is set small.

[0034] Further, an opening 21a is formed at a substantially central position at the top of the bent portion of the second tank plate 21, and the top is joined to the inner surface (upper inner surface) of the cooling water tank 5c. The opening 21a and the connector 24 are fitted. Further, an L-shaped engagement claw 21b extending downward is provided at the edge of the second tank plate 21. The engagement claw 21b is formed on the lower surface of the second tank plate 21. Hold the first tank plate 22 placed in close contact with the side.

[0035] The pair of closing plates 23 are arranged at both open ends of the cylindrical space (tank passage 26) between the first tank plate 22 and the second tank plate 21, and close the tank passage 26. To do. The shape of the closing plate 23 is substantially in line with the shape of the inner surface of the bent portion of the second tank plate 21.

[0036] The refrigerant tank 20B on the outlet side includes a pipe portion formed by assembling the first tank plate 22 and the second tank plate 21, and a pair of closures that close both end openings of the pipe portion. And plate 23. The refrigerant tank 20B on the outlet side supplies the refrigerant from the core side to the refrigerant air cooling unit 7 of the condenser via a tank passage 26 formed inside. The outlet side refrigerant tank 20B has the same configuration as that of the inlet side refrigerant tank 20A, and is provided in the cooling water tank 5c with the inlet side refrigerant tank 20A turned upside down. The refrigerant tank 20B on the outlet side contacts the lower wall of the cooling water tank 5c. Are joined together by brazing.

[0037] The core of the refrigerant water cooling unit 8 is composed of a plurality of refrigerant flat tubes 10. Each of the refrigerant flat tubes 10 is formed so that the inside thereof is hollow along the longitudinal direction, whereby a refrigerant passage is formed inside, and openings of the refrigerant passage are formed at both ends in the longitudinal direction. Each flat tube 10 is arranged such that its longitudinal direction is in the vertical direction. An inner fin 14 is accommodated in the flat tube 10. The total length of the inner fin 14 is shorter than the total length of the flat tube 10. For this reason, both ends of the inner fin 14 in the longitudinal direction are on the inner side in the longitudinal direction of the flat tube 10 than both ends of the flat tube 10 in the longitudinal direction. Here, the protruding length of both ends in the longitudinal direction of the flat tube 10 protruding from both ends in the longitudinal direction of the inner fin 14 is set to be equal to or less than the thickness of the second tank plate 21.

[0038] Each refrigerant flat tube 10 has one end in the longitudinal direction inserted into the tube insertion hole 22c of the first tank plate 22 in the refrigerant tank 2OA on the inlet side, and the second tank The plate 21 is joined by brazing while being in contact with the lower surface (tank inner surface) of the plate 21. Each of the refrigerant flat tubes 10 has its other longitudinal end inserted into the tube insertion hole 22c of the first tank plate 22 in the refrigerant tank 20A on the inlet side. Joined by brazing while being in contact with the lower surface of the plate 21 (inner surface of the tank). As a result, the individual refrigerant flat tubes 10 are laminated in a direction perpendicular to the flow direction of the cooling water in a state where the short side direction (the width direction thereof) is arranged in parallel with the flow direction of the cooling water. Yes.

[0039] Each refrigerant flat tube 10 is formed with beads 12a and 12b projecting outward on both flat surfaces, and the adjacent refrigerant flat tubes 10 are abutted against each other. Joined by brazing in the state. Further, a bead 30 is formed on the inner peripheral surface of the cooling water tank 5c so that the inner peripheral surface partially protrudes inward, and the beads 12a and 12b of the refrigerant flat tube 10 located on the outermost side, The bead 30 is joined to the cooling water tank 5c-side bead 30 by brazing. For this reason, at the time of brazing, if a load is applied from the outside of the cooling water tank 5c, the flat tube 10 and the inner fin 14 can be joined in a close contact state. FIG. 7 is an exploded perspective view illustrating an assembled state of the sub radiator 5. When assembling the sub-radiator 5, heat radiation fins 5b and flat tubes 5a for cooling water are alternately stacked, and a reinforcement 5d is installed outside the outermost fins, with an appropriate amount of load applied in the stacking direction. The ends of the cooling water flat tube 5a and the reinforcement 5d are inserted into the upstream cooling water tank 5c and the downstream cooling water tank 5c, respectively. The cooling water tank 5c on the downstream side is configured by assembling a substantially box-shaped tank body 51 having an opening on the side of the cooling water flat tube 5a and a closing portion 52 for closing the opening of the tank body 51. Thus, the coolant cooling unit 8 can be incorporated into the tank body 51 with the closing part 52 open.

[0041] Then, the connector 24 serving as the refrigerant inlet of the refrigerant water cooling unit 8 is fitted to the upper wall of the cooling water tank 5c, and the connector 25 serving as the refrigerant outlet of the refrigerant water cooling unit 8 is fitted to the lower wall. Then, a connector 53 serving as a cooling water outlet of the cooling water tank 5c is fitted to the side wall (52) opposite to the side wall (52) into which the cooling water flat tube 5a is inserted.

[0042] The sub radiator 5 in which the individual parts are assembled and the refrigerant water cooling unit 8 is built in is heated in a heating furnace, so that the brazing material provided in advance at the joint between these various parts is used. The brazing is performed integrally. The refrigerant water cooling section 8 has a larger heat capacity than other parts, and it may be difficult to perform integral brazing. In this case, the refrigerant water cooling section 8 and a part of the upstream side cooling water tank 5c are assembled as separate bodies, and then brazed, and then assembled into the sub radiator body and brazed. Good.

[0043] The cooling water that has cooled the electric drive unit 4 in the vehicular composite heat exchanger 1 having such a configuration is provided in the cooling water tank 5c on the upstream side of the sub radiator 5. From the inlet-side connector 54, and then flows through each of the cooling water flat tubes 5a and into the downstream cooling water tank 5c. In the process of flowing through the cooling water flat tubes 5a, the cooling water is transferred from the cooling water flat tubes 5a to the radiating fins 5b and from the radiating fins 5b to the cooling air to perform heat exchange. Thereby, the cooling water is cooled. The cooling water whose temperature has decreased flows between the individual refrigerant flat tubes 10 in the refrigerant water cooling section 8 in the cooling water tank 5 c on the downstream side, and then flows out from the connector 53.

[0044] The refrigerant circulating in the refrigeration cycle is a high-temperature and high-pressure gas discharged from the compressor. In this state, the refrigerant flows into the coolant cooling unit 8 through the connector 24. The refrigerant flowing into the refrigerant water cooling unit 8 first flows into the upper refrigerant tank 20A on the refrigerant inlet side, and is dispersed from the upper refrigerant tank 20A on the refrigerant inlet side to each refrigerant flat tube 10. The heat of the refrigerant flowing in the refrigerant flat tube 10 is transferred to the cooling water from the refrigerant flat tube 10 and becomes the refrigerant outlet side when the degree of superheat is reduced or partially enters the saturated region. Flows into the lower refrigerant tank 20B. Then, the refrigerant is discharged from the lower refrigerant tank 20B on the refrigerant outlet side to the outside of the refrigerant water cooling unit 8 via the connector 25, and then flows into the refrigerant tank upstream of the refrigerant air cooling unit 7 of the condenser 6. .

[0045] Normally, water cooling has a higher heat transfer efficiency than air cooling, and the size can be reduced. However, when the refrigerant is completely condensed with cooling water, the temperature difference between the refrigerant condensing temperature and the cooling water is small. Therefore, in order to cover all the cooling of the refrigerant by water cooling, there is a possibility that the core part of the sub-radiator 5 and the refrigerant water cooling part 8 are increased in size. However, in the present embodiment, in addition to the refrigerant water cooling unit 8, the refrigerant air cooling unit 7 is used in combination, so that the sub radiator 5 and the refrigerant water cooling unit 8 can be prevented from being enlarged. In addition, the refrigerant flowing into the refrigerant water cooling unit 8 has a high temperature of the refrigerant that is downstream of the compressor and upstream of the refrigerant air cooling unit 7. Further, the cooling water flowing into the refrigerant water cooling unit 8 radiates heat at the core of the sub radiator 5. Since this is the cooling water after the cooling, the temperature of the cooling water is lowered. Therefore, the temperature difference between the cooling water and the refrigerant that exchange heat with each other in the refrigerant water cooling unit 8 is increased, the heat exchange efficiency is improved, and the size of the refrigerant water cooling unit 8 can be suppressed.

[0046] According to the present embodiment, in the coolant water cooling section 8, a bent portion is formed in the central region of the second tank plate 21, and the curvature of the bent portion is reduced, whereby the width of the in-tank passage 26 is reduced. L 1 is set to a value smaller than the width L 2 of the refrigerant flat tube 10. As a result, the strength against the internal pressure is improved in the refrigerant tank 20A on the inlet side and the refrigerant tank 20B on the outlet side, and the tank plates 22 and 21 can be made thinner accordingly. When the tank plates 22 and 21 are thinned as described above, the coolant water cooling section 8 can be reduced in weight, and the difference in heat capacity from the peripheral portion such as the cooling water tank 5c of the sub radiator 5 is reduced, thereby improving the brazing performance. That's the power S.

[0047] Also, by reducing the thickness of the tank plates 22 and 21, the refrigerant tank 20A on the inlet side and the outlet The vertical dimension of the refrigerant tank 20B on the mouth side can be reduced. In this way, when the vertical dimensions of the inlet side refrigerant tank 20A and the outlet side refrigerant tank 20B are reduced, the refrigerant flat tube 10 can be set longer, so that the efficiency of heat exchange can be improved.

Further, according to the present embodiment, the longitudinal end of the refrigerant flat tube 10 is inserted into the tube insertion hole 22c of the first tank plate 22, and then the second tank plate 21 Bonded to the bottom surface. Therefore, the strength of the connecting portion between the refrigerant flat tube 10 and the inlet side refrigerant tank 20A or the outlet side refrigerant tank 20B is further improved.

Further, according to the present embodiment, the inner fin 14 is set slightly shorter than the flat tube 10, so that the tip of the flat tube 10 abuts against the second tank plate 21. A refrigerant passage can be secured.

Further, according to the present embodiment, the inner fin 14 is shorter than the flat tube 10, and a portion where the inner fin 14 is not joined is generated at the longitudinal end portion of the flat tube 10. However, in this embodiment, the distance between the flat tubes 10 where the inner fins 14 are not provided is equal to or less than the thickness of the first tank plate 22. Therefore, it is reinforced by the first tank plate 22 and the strength reduction can be suppressed.

[0051] Here, for example, in a structure in which the upper wall of the cooling water tank 5c and the refrigerant tank 20A are separated from each other and the lower wall of the cooling water tank 5c and the refrigerant tank 20B are separated from each other, the upper wall of the cooling water tank 5c and Cooling water flows between the refrigerant tank 20A and between the lower wall of the cooling water tank 5c and the refrigerant tank 20B, toward the refrigerant flat tube 10 between the refrigerant tanks 20A and 20B. The cooling water does not flow and heat exchange efficiency may decrease.

[0052] However, in the present embodiment, the refrigerant tank 20A on the inlet side of the refrigerant water cooling section 8 is brazed and joined to the upper wall of the cooling water tank 5c in the cooling water tank 5c of the sub radiator 5. The refrigerant tank 20B on the outlet side is brazed to the lower wall of the water tank 5c. Therefore, it is possible to prevent the cooling water from flowing between the upper wall of the cooling water tank 5c and the refrigerant tank 20A and between the lower wall of the cooling water tank 5c and the refrigerant tank 20B. The refrigerant can be circulated between a plurality of multi-stage refrigerant flat tubes 10 between the tank 20A and the refrigerant tank 20B. Thereby, heat exchange efficiency increases.

[0053] Further, for example, the cooling air flow in the outer wall of the cooling water tank on the downstream side of the sub radiator A method may be considered in which the refrigerant flows into and out of the refrigerant water cooling section 8 from the upper side surface. However, according to the force and the method, the refrigerant line pipe jumps out to the windward side of the sub radiator 5 and becomes an obstacle in the layout.

On the other hand, in the present embodiment, the refrigerant in and out of the refrigerant water cooling unit 8 is entered from above the cooling water tank 5c and is taken out from below. Therefore, it is advantageous in terms of layout and can be finished in a smart appearance. In addition, the refrigerant can be smoothly guided to the refrigerant air cooling unit 7 of the capacitor 6 located below the sub radiator 5.

In the present embodiment, the cooling water tank 5c on the downstream side of the sub radiator 5 and the refrigerant tank 7c on the upstream side of the refrigerant air cooling unit 7 of the condenser 6 are coupled by brazing. Therefore, the coupling between the sub radiator 5 and the refrigerant air cooling part 7 of the condenser 6 can be easily strengthened, and a coupling bracket or the like is not required, so that the configuration can be simplified. Furthermore, it is also possible to share a patch end that closes each tank between the cooling water tank 5c of the sub radiator 5 and the cooling tank on the upstream side of the refrigerant air cooling unit 7 of the condenser 6.

Further, in the present embodiment, as shown in FIG. 7, the width L3 along the stacking direction of the refrigerant flat tubes 10 in the core portion of the refrigerant water cooling portion 8 is equal to that of the flat tubes 5a for the cooling water in the sub radiator 5. Width (length in the short side direction of the flat tube) L4 or less. Therefore, it is possible to suppress the size force S along the ventilation direction of the cooling water tank 5c on the downstream side of the sub radiator 5 and to be larger than the cooling water tank 5c on the upstream side, thereby improving the layout.

Next, the feature points of this embodiment will be listed.

[0058] (1) The composite heat exchanger of the present embodiment includes a core portion in which a plurality of cooling water flat tubes 5a are stacked in multiple stages, and a cooling water tank 5c into which cooling water that has passed through the core portion flows. The cooling water heat exchanger 5 and the cooling water tank 5c of the cooling water heat exchanger 5 are installed in the cooling water tank 5c. And a refrigerant water cooling section 8 for exchanging heat with the cooling water. The refrigerant water cooling section 8 has a core section in which a plurality of refrigerant flat tubes 10 are stacked in multiple stages, and a tank passage 26 extending in the stacking direction of the refrigerant flat tubes 10 and is used for the refrigerant. Longitudinal direction of the flattened tube 10 The first refrigerant tank 20A communicated with one end, a tank internal passage 26 extending in the stacking direction of the flattened tube for refrigerant 10, and the longitudinal direction of the flattened tube for refrigerant 10 other And a second refrigerant tank 20B in which the open end of the other side is connected in communication. In the first refrigerant tank 20A and the second refrigerant tank 20B, the width L1 of the tank passage 26 is set to be the refrigerant flat tube along the width direction (short side direction) of the refrigerant flat tube 10. Less than 1 0 width L2.

[0059] Therefore, in the first and second refrigerant tanks 20A and 20B, the strength against the internal pressure is improved, and accordingly, the members constituting the refrigerant tanks 20A and 20B can be thinned. As a result, the first and second refrigerant tanks 20A and 20B have a smaller heat capacity difference from the peripheral parts, so that the brazing performance can be improved.

That is, according to the present embodiment, it is possible to reduce the size while ensuring the strength of the refrigerant tanks 20A and 20B, improve the layout, and improve the manufacturability.

[0061] Further, as the members constituting the first and second refrigerant tanks 20A and 20B are made thinner, the longitudinal dimension of the refrigerant flat tube 10 between the refrigerant tanks 20A and 20B can be increased. The heat exchange efficiency can be improved.

[0062] (2) In the present embodiment, the outline of the cross-sectional shape of the tank passage 26 has an arc shape, so that the width L1 of the tank passage 26 is greater than the width L2 of the refrigerant flat tube. Is set too small.

[0063] (3) In the present embodiment, the flat tube 10 has one end in the longitudinal direction abutted against the inner surface of the first refrigerant tank 20A, and the other end in the longitudinal direction is the second tube. It is abutted against the inner surface of the refrigerant tank 20B. Therefore, the connection strength between the flat tube 10 and the first and second refrigerant tanks 20A and 20B is further improved.

[0064] (4) Here, for example, one longitudinal end of the cooling water tank 5c (the upper wall of the cooling water tank 5c) and the cooling medium tank 20A are separated from each other, and the other longitudinal end of the cooling water tank 5c (the cooling water tank). In the structure in which the lower wall of 5c and the refrigerant tank 20B are separated from each other, the longitudinal end of the cooling water tank 5c and the refrigerant tank 20A and the other longitudinal end of the cooling water tank 5c and the refrigerant tank 20B are separated. Cooling water will flow between them. In other words. There is a possibility that the cooling water does not flow toward the refrigerant flat tube 10 between the two refrigerant tanks 20A and 20B, and the heat exchange efficiency is lowered.

However, in the present embodiment, the first refrigerant tank 20A is placed in the cooling water tank 5c. The second refrigerant tank 20B is in contact with one end in the longitudinal direction of the cooling water tank 5c (upper wall of the cooling water tank 5c), and the other end in the longitudinal direction of the cooling water tank 5c (cooling water) It is in contact with the lower wall of the tank 5c. Therefore, it is possible to prevent the cooling water from flowing between the upper wall of the cooling water tank 5c and the refrigerant tank 20A and between the lower wall of the cooling water tank 5c and the refrigerant tank 20B. The refrigerant can be circulated toward the refrigerant flat tube 10 between the refrigerant tank 20A and the refrigerant tank 20B. As a result, the heat exchange efficiency is increased and the coolant water cooling unit 8 can be downsized.

(5) In the present embodiment, the refrigerant discharged from the compressor of the refrigeration cycle flows into the refrigerant water cooling unit 8. Therefore, since the refrigerant flowing into the refrigerant water cooling unit 8 is a high-temperature and high-pressure refrigerant, the temperature difference from the cooling water flowing outside the refrigerant water cooling unit 8 can be increased.

[0067] Thereby, the cooling efficiency is improved, and the refrigerant water cooling unit 8 can be prevented from being enlarged.

[0068] (6) Further, in the present embodiment, the condenser 6 of the refrigeration cycle for circulating the refrigerant is further provided, and the condenser 6 includes the refrigerant water cooling unit 8 and the refrigerant air cooling unit 7. Yes. Therefore, the refrigerant air cooling unit 7 and the refrigerant water cooling unit 8 complement each other, and the refrigerant air cooling unit 7 and the refrigerant water cooling unit 8 can be made compact.

(7) In the present embodiment, the refrigerant flowing through the capacitor 6 flows in the order of the refrigerant water cooling unit 8 and the refrigerant air cooling unit 7. Therefore, in the structure including the refrigerant air cooling unit 7, the refrigerant flowing into the refrigerant water cooling unit 8 is a high-temperature and high-pressure refrigerant downstream of the compressor and upstream of the refrigerant air cooling unit 7. Therefore, the temperature difference between the cooling water and the refrigerant that exchange heat with each other in the refrigerant water cooling unit 8 increases. Therefore, the cooling efficiency of the refrigerant water cooling unit 8 is improved, and the enlargement of the refrigerant water cooling unit 8 can be suppressed.

[0070] (8) In the present embodiment, the cooling water flowing into the refrigerant water cooling unit 8 is the cooling water after the heat is radiated from the core of the sub radiator 5, so the temperature of the cooling water is low. As a result, the temperature difference between the cooling water and the refrigerant that exchange heat with each other in the refrigerant water cooling section 8 increases. Therefore, the cooling efficiency of the refrigerant water cooling unit 8 is improved, and an increase in the size of the refrigerant water cooling unit 8 can be suppressed.

Yes

(9) In the present embodiment, the cooling water tank 5c is connected to the refrigerant tank 7c of the refrigerant air cooling unit 7. It is joined. Therefore, the coupling between the cooling water heat exchanger 5 and the refrigerant air cooling unit 7 can be easily strengthened. Since a coupling bracket or the like is required, the configuration can be simplified.

(10) In this embodiment, the width L3 of the core portion of the coolant water cooling section 8 is equal to or less than the width L4 of the coolant flat tube 5a along the stacking direction of the coolant flat tubes 10. It is. Therefore, the cooling water tank 5c on the downstream side of the cooling water heat exchanger 5 can be suppressed from becoming larger than the cooling water tank 5c on the upstream side, and the layout can be improved.

(10) In the present embodiment, the cooling water heat exchanger (5) cools the electric drive section (4).

[0074] (Second Embodiment)

FIG. 8 is a front view schematically showing the configuration of the refrigerant water cooling unit 8 in the second embodiment, and FIG. 9 is a side view schematically showing the configuration of the refrigerant water cooling unit 8 according to the second embodiment. . The refrigerant water cooling unit 8 according to the first embodiment is different from that according to the first embodiment in the shapes of the refrigerant tank 20A on the inlet side and the refrigerant tank 20B on the outlet side. In addition, about the same structure as 1st Embodiment, a referential mark is quoted and the overlapping description is abbreviate | omitted.

[0075] The inlet-side refrigerant tank 20A includes a pair of tank plates 21 and 22 and a pair of patch ends (not shown).

[0076] The second tank plate 21 is a flat plate having a substantially rectangular shape. The second tank plate 21 has an opening substantially in the center thereof, and the upper surface side of the second tank plate 21 is joined to the inner surface of the upper wall of the cooling water tank 5c so that the opening and the connector 24 are connected. Mating. An L-shaped engaging claw 21b extending downward is provided at the edge of the second tank plate 21. The engaging claw 21b is provided on the lower surface side of the second tank plate 21. Hold the first tank plate 22 placed in close contact with the tank.

[0077] The first tank plate 22 is a plate-like member having a substantially rectangular shape corresponding to the outer shape of the second tank plate 21. The first tank plate 22 has a bent portion that is curved in a convex shape toward the inner side in the longitudinal direction of the flat tube for cooling medium 10 (toward the side facing the connector 24). ing. By this bent portion, a space in which the outline of the cross-sectional shape has an arc shape is formed in the first tank plate 22. This space extends in the stacking direction of the flat tubes 10. This space cores the refrigerant It functions as an in-tank passage 26 for supplying to the section. The width L1 of the tank passage 26 is set smaller than the width L2 of the refrigerant flat tube 10 as in the first embodiment. Further, the second tank plate 21 has a rectangular tube insertion hole, which corresponds to the outer peripheral shape of the refrigerant flat tube 10 and corresponds to the tube insertion hole. The longitudinal end of the refrigerant flat tube 10 is fitted.

[0078] The configuration of the outlet side refrigerant tank 20B is the same as that of the inlet side refrigerant tank 20A, and is provided in the cooling water tank 5c with the refrigerant tank 20A on the inlet side turned upside down. Yes. The refrigerant tank 20B on the outlet side is joined to the lower wall of the cooling water tank 5c by brazing.

[0079] At both ends in the longitudinal direction of each flat tube 10 for refrigerant, the central portion in the width direction of the flat tube 10 (= the central portion in the short side direction of the flat tube 10) is paired in shape with the passage 26 in the tank. Correspondingly, the shape is cut into a substantially semicircular shape. Both ends in the longitudinal direction of each of the refrigerant flat tubes 10 having such a shape are expanded in the thickness direction of the flat tubes 10 (= the stacking direction of a plurality of flat tubes 10) and are adjacent to each other in the stacking direction. The refrigerant flat tubes 10 are directly joined to each other.

[0080] One end of the refrigerant flat tube 10 in the longitudinal direction is inserted into the opening (see reference numeral 27 in Fig. 23) of the first tank plate 22 in the refrigerant tank 20A on the inlet side, and the second tube 10 Joined by brazing while being in contact with the lower surface of the tank plate 21 (inner surface of the tank). In addition, each of the refrigerant flat tubes 10 is inserted into the opening of the first tank plate 22 in the refrigerant tank 20B on the outlet side (see reference numeral 27 in FIG. 23) at the other end in the longitudinal direction. The tank plate 21 is abutted against the upper surface (the tank inner surface) and joined by brazing.

As described above, according to the present embodiment, the same effects as those of the first embodiment are obtained, and the following further effects are obtained.

In the second embodiment, the refrigerant flat tubes 10 adjacent to each other in the stacking direction are directly joined to each other by expanding both longitudinal ends of the refrigerant flat tubes 10 in the thickness direction of the tubes 10. Yes. Therefore, one opening (see reference numeral 27 in FIG. 23) is used to insert a set of refrigerant flat tubes 10 in which a plurality of first tank plates 22 are stacked in multiple stages. A square frame shape having a light source). As a result, it is possible to simplify the shape of the first tank plate 22 without having to machine tube insertion holes (see reference numeral 22c in FIG. 6) corresponding to the number of refrigerant flat tubes 10 in the first tank plate 22. .

In the second embodiment, the pressure loss when the tube enters and exits can be reduced by expanding the both ends in the longitudinal direction of the refrigerant flat tube 10.

[0084] Further, in the second embodiment, the individual refrigerant flat tubes 10 are abutted against the flat plate-like second tank plate 21, thereby increasing the size of the refrigerant flat tubes 10 in the longitudinal direction. Power S can be. As a result, the heat radiation surface of the refrigerant flat tube 10 can be increased, so that the heat exchange region can be widened.

[0085] (Third embodiment)

FIG. 10 is a perspective view schematically showing a composite heat exchanger for a vehicle according to a third embodiment of the present invention. The vehicle combined heat exchanger of the third embodiment is different from that of the first or second embodiment in that a refrigerant water cooling unit 70 is used instead of the refrigerant water cooling unit 8. Note that the same configurations as those in the first or second embodiment are referred to with reference numerals, and detailed descriptions thereof are omitted, and the following description is focused on the differences.

[0086] The refrigerant water cooling unit 70 constitutes a part of the refrigerant line between the compressor and the refrigerant air cooling unit 7 of the capacitor 6 in the refrigeration cycle of the air conditioning system. The refrigerant water cooling unit 70 is directly attached to the cooling water tank 5c on the downstream side of the sub radiator 5. Cooling water from the cooling water tank 5c flows into the refrigerant water cooling section 70, and refrigerant from the refrigeration cycle compressor flows. In the coolant cooling unit 70, heat exchange is performed between the coolant and the coolant, thereby cooling the coolant.

FIG. 12 is a side view schematically showing shell plates 76 and 77 constituting refrigerant water cooling unit 70, and FIG. 13 is a cross sectional view of refrigerant water cooling unit 70 along the AA cross section in FIG. It is.

[0088] As shown in FIG. 13, the refrigerant water cooling section 70 is configured by stacking a plurality of sets of first shell plates 76 and second shell plates 77 facing each other, and each shell plate 76 and 77 have a flat plate shape as a whole. The first and second shell plates 76 and 77 are formed of a member having excellent thermal conductivity, for example, a metal plate such as an aluminum alloy. [0089] The first shell plate 76 and the second shell plate 77 are laminated so that the plate surfaces are orthogonal to the longitudinal direction of the flat tube 10 of the sub radiator 5. Further, the first shell plate 76 and the second shell plate 77 are arranged so that their plate surfaces are orthogonal to the inflow direction of the cooling water from the cooling water tank 5c.

[0090] The peripheral portions of the first and second shell plates 76 and 77 are bent in a substantially L shape, and the peripheral portions are joined to each other by brazing. In the set of the first shell plate 76 and the second shell plate 77 joined to each other, the sets adjacent to each other are joined by brazing via the peripheral edge. Here, the cooling water tank 5c on the downstream side of the radiator 5 has an open side wall on the outer side in the longitudinal direction of the refrigerant flat tube 10 of the sub radiator 5. The cooling water tank 5c side is located at the inner periphery of the opening. The peripheral edge portion of the first shell plate 76E located at is joined by brazing. Thereby, the cooling water tank 5c and the coolant cooling unit 70 are integrated.

In the refrigerant water cooling section 70 having such a configuration, a space between a pair of shell plates 76 and 77 adjacent in the stacking direction is formed as a passage for cooling water or refrigerant. In each of the passages, a first passage 78 through which a coolant flows and a second passage 79 through which cooling water flows are alternately set in the stacking direction of the shell plates 76 and 77. Each first passage 78 is provided with an inner fin 80! /.

Further, as shown in FIG. 13, the coolant cooling section 70 includes a cooling water inlet passage 81 that passes through the individual shell plates 76 and 77, and a cooling water outlet passage 82. When the cooling water from the cooling water tank 5c flows into the cooling water inlet passage 81, the force of the cooling water inlet passage 81 is also branched to the individual second passages 79. The refrigerant that has flown through the individual second passages 79 joins the cooling water outlet passage 82 and flows out to the outside (electric drive unit 4 side) via the cooling water outlet passage 82 (Clout). ).

Here, as shown in FIG. 12, the first shell plate 76 and the second shell plate 77 have openings 76a and 77a corresponding to the cooling water inlet passage 81 and the cooling water outlet passage 82, respectively. Each is formed. The peripheral portion of the opening 76a of the first shell plate 76 is formed with a concave portion that is recessed in a concave shape toward the outside (right side in FIG. 13). The peripheral portion of the opening 76a of the first shell plate 76 configured in this manner is connected to the adjacent second shell plate. 77 (the second shell plate 77 located on the right side in FIG. 13) is brought into contact with the peripheral edge of the opening 77a and joined by brazing, so that the cooling water inlet passage 81 and the cooling A water outlet passage 82 is formed as a continuous passage.

Similarly, as shown in FIG. 13, the refrigerant water cooling section 70 includes a refrigerant inlet passage 83 and a refrigerant outlet passage 84 that penetrate through the individual shell plates 76 and 77. When the refrigerant (C2in) from the compressor flows into the refrigerant inlet passage 83, it branches to the individual first passages 78 via the refrigerant inlet passage 83. The refrigerant flowing through the individual first passages 78 joins the refrigerant outlet passages 84 and flows out to the outside (the refrigerant air cooling unit 7 side) via the refrigerant outlet passages 84 (C2out). .

Here, as shown in FIG. 12, the first shell plate 76 and the second shell plate 77 have openings 76b and 77b corresponding to the refrigerant inlet passage 83 and the refrigerant outlet passage 84, respectively. Has been. A peripheral portion of the opening 77b of the second shell plate 77 is formed with a concave portion that is recessed in a concave shape toward the outside (right side in FIG. 13). The peripheral edge of the opening 77b of the second shell plate 77 configured in this way is the peripheral edge of the opening 76b of the adjacent first shell plate 76 (the first shell plate 76 located on the right side in FIG. 13). The refrigerant inlet passage 83 and the refrigerant outlet passage 84 are formed as a continuous passage by bringing the contact portions into contact with each other and joining the contact portions by brazing.

[0096] In the present embodiment, the outermost shell plate 76E on the cooling water tank 5c side (Fig.

The leftmost first shell plate 76E) in FIG. 13 includes an opening 76b corresponding to the refrigerant inlet passage 83, an opening 76b corresponding to the refrigerant outlet passage 84, and the cooling in the normal first shell plate 76. The opening 76a corresponding to the water outlet passage 82 is closed.

[0097] The outermost shell plate 77E on the opposite side to the cooling water tank 5c (the rightmost second shell plate 77E in FIG. 13) is the cooling water in the normal second shell plate 77. The opening 77a corresponding to the inlet passage 81 is closed.

In the present embodiment, the cooling water inlet passage 81 is laid out below the refrigerant water cooling unit 70, and the cooling water outlet passage 82 is laid out above the refrigerant water cooling unit 70. Therefore, in the coolant cooling section 70, the cooling water flows through the second passage 79 from below to above. On the other hand, the refrigerant inlet passage 83 is arranged above the refrigerant water cooling unit 70. The refrigerant outlet passage 84 is laid out below the refrigerant water cooling section 70. Therefore, in the refrigerant water cooling unit 70, the refrigerant flows through the first passage 78 from the upper side to the lower side. Therefore, the refrigerant and the cooling water flow in directions opposite to each other in the refrigerant water cooling unit 70.

[0099] As shown in FIG. 12, the cooling water inlet passage 81 and the cooling water outlet passage 82 are offset in the horizontal direction (left-right direction in FIG. 12) on a plane orthogonal to the passage extending direction. . Further, both the refrigerant inlet passage 83 and the refrigerant outlet passage 84 are offset in the horizontal direction (left-right direction in FIG. 12) on a plane orthogonal to the passage extending direction. For this reason, the traveling direction of refrigerant and cooling water intersect each other (see Fig. 12).

[0100] With such a configuration, the cooling water that has cooled the electric drive unit 4 flows into the cooling water tank 5c on the upstream side through the cooling water inlet 54 of the sub radiator 5, and then, each cooling water flat It flows through the tube 5a and flows into the cooling water tank 5c on the downstream side. In the process where the cooling water flows through the cooling water flat tube 5a !, the heat of the cooling water is transmitted to the cooling water flat tube 5a and the heat radiation fin 5b and from the heat radiation fin 5b to the cooling air. Heat exchange. Thereby, the cooling water is cooled. The cooling water that has flowed to the cooling water tank 5c on the downstream side passes through the refrigerant water cooling unit 70 from there. Specifically, the cooling water from the cooling water tank 5c on the downstream side branches from the cooling water inlet passage 81 to the individual second passages 79, and flows through the second passages 79, respectively. They merge at the outlet passage 82 and are then supplied to the electric drive unit 4 side.

[0101] Further, the refrigerant circulating in the refrigeration cycle of the air conditioning system flows into the refrigerant water cooling unit 70 in the state of high-temperature and high-pressure gas discharged from the compressor. Specifically, the refrigerant that has flowed into the refrigerant water cooling unit 70 branches from the refrigerant inlet passage 83 to the individual first passages 78 and flows through the first passages 78. The refrigerant flowing in the first passage 78 is transferred to the cooling water by the heat power S inner fin 80 force, the first and second cheno replay rods 76, 77, the first and second cheno repre plate rods 76, 77, and so on. Heat is dissipated and the degree of superheat is reduced, or it enters a state where it is partially saturated. The refrigerant flowing through the individual first passages 78 merges in the refrigerant outlet passage 84 and then flows into the refrigerant air cooling unit 7.

[0102] The main feature points of the third embodiment are listed below. [0103] The composite heat exchanger 1 of the present embodiment circulates the first fluid (cooling water) between the first heat generator 4 and the heat of the first heat generator via the first fluid. A first heat exchanger 5 (a stabulator) that radiates heat and having a first fluid tank 5c through which the first fluid flows, and a second heating element (compressor) A second heat exchanger 7 (refrigerant air cooling unit) that radiates heat of the second heating element through the second fluid by circulating a second fluid (refrigerant) therebetween, and the second heating element ( Compressor) and the second heat exchanger 7 to form a part of the second fluid line (refrigeration cycle) for circulating the second fluid, and attached to the first fluid tank 5c and A second fluid that exchanges heat between the first fluid from the first fluid tank 5c and the second fluid by being connected to the first fluid tank 5c.却部 has 70 (the refrigerant water-cooling unit), the. The second fluid cooling unit 70 includes first plate 76 and second plate 77 having a plate shape in which the inflow direction of the first fluid from the first fluid tank 5c and the plate surface are orthogonal to each other. The first plate and the second plate are separated from each other and the peripheral edge thereof is liquid-tightly joined. Between the plates 76 and 77 adjacent to each other, the second fluid is directed toward the plate stacking direction. The first passage 78 through which the first fluid flows and the second passage 79 through which the first fluid flows are alternately provided.

[0104] Therefore, before the second fluid flows into the second heat exchanger 7, the second fluid passes through the first heat exchanger 5 to the second fluid cooling unit 70! Cooling efficiency is improved because the first fluid can be used for cooling.

[0105] Further, since the second fluid cooling section 70 has a laminated structure of shell plates 76, 77, the second fluid cooling section 70 can be downsized while ensuring the strength of the second fluid cooling section 70. In addition, since the second fluid cooling section 70 has a laminated structure of the shell plates 76 and 77, the refrigerant individual plates 76 and 77 can be easily assembled together. As a result, the brazing clearance management is reduced and the brazing performance is improved.

[0106] Also, according to the present embodiment, the first fluid tank 5c is formed in a box shape in which one side surface is formed as an opening, and the second fluid cooling unit is formed at the peripheral edge of the opening of the first fluid tank 5c. The peripheral edge of 70 is joined to close the opening. For this reason, the first fluid tank 5c and the second fluid cooling section 70 can be integrated with a simple structure, thus saving space. [0107] Further, according to the present embodiment, the first heat exchanger 5 is for the first fluid that exchanges heat between the first fluid and air by circulating the first fluid therein. The second passage 79 of the refrigerant water cooling unit 70 is connected to the downstream side of the flat tube 5a via the first fluid tank 5c. Further, the first passage 78 of the refrigerant water cooling unit 70 is upstream of the second heat exchanger 7 in the second fluid line (refrigeration cycle). Therefore, the temperature difference between the first fluid flowing through the second passage 79 and the second fluid flowing through the first passage 78 becomes large, and the heat exchange efficiency is improved.

Further, according to the present embodiment, the flow of the first fluid (cooling water) and the second fluid (refrigerant) are opposed in the second fluid cooling section. Therefore, the heat exchange efficiency can be improved.

[0109] Also, according to the present embodiment, the first fluid (cooling water) flows upward in the second fluid cooling section 70, so even when the flow rate of the first fluid (cooling water) is small, The deterioration of the flow distribution can be relatively suppressed.

[0110] Also, according to the present embodiment, in the second fluid cooling section 70, the refrigerant circulating through the refrigeration cycle as the second fluid is caused to flow downward, so that the oil contained in the refrigerant is the second fluid. It is advantageous for the oil to easily return to the compressor that includes many sliding parts that stay in the fluid cooling unit 70.

[0111] Also, according to the present embodiment, the second fluid outlet (refrigerant outlet 84) in the second fluid cooling section 70 is laid out on the lower side, so that the second fluid cooling section 70 is positioned below the second fluid cooling section 70. The distance to the second heat exchanger 7 is reduced, and both can be connected smoothly.

Further, according to the present embodiment, the inner fin 80 is installed in the first passage 78 of the second fluid cooling unit 70. The heat exchange efficiency between the first fluid and the second fluid can be improved.

[0113] In the present embodiment, the inner fin 80 is arranged only on the first passage 78 side, but it may be arranged on the second passage 79 side. Of course, without using the inner fins 80, the first and second shell plates 76, 77 may be provided with irregularities (beads) so as to ensure a heat radiation area and strength. In this case, the number of parts can be reduced and the assembly time can be reduced.

[0114] In the present embodiment, the first and second shell plates 76 and 77 are alternately arranged. In this case, it is possible to further reduce the number of types of parts.

[0115] Further, the sub radiator 5 and the coolant cooling unit 70 are not necessarily integrated by brazing. For example, if the structure is made by brazing the two parts separately and then crimping the periphery with the packing in between, it is possible to achieve more appropriate brazing conditions for each, and brazing Can be achieved.

[0116] As described above, the refrigerant water cooling unit 8 (or the refrigerant water cooling unit 70) of the first to third embodiments performs heat exchange between the cooling water that cools the electric drive unit 4 and the refrigerant of the refrigeration cycle. However, the present invention is not limited to this, and heat exchange can be performed between the first fluid that cools the first heating element and the second fluid that cools the second heating element.

[0117] (Fourth embodiment)

Next, a fourth embodiment will be described with reference to FIGS. Fig. 14 is a block diagram of the combined heat exchanger 1 for a vehicle, Fig. 15 is a schematic perspective view of the combined heat exchanger 1 for a vehicle, and Fig. 16 is a refrigerant water cooling section (water cooling) installed in the tank 5c of the sub-rajator 5. Fig. 17 is a side view of the refrigerant water cooling unit (water-cooled capacitor) installed in the sub radiator tank, and Fig. 18 is an exploded view of the main part of the refrigerant water cooling unit (water-cooled capacitor). FIG. 19 (a) is a perspective view of the main part showing the arrangement of the inner fins in the tube, and FIG. 19 (b) is a front view of the main part of the inner fins.

[0118] The refrigerant water-cooling section (water-cooled condenser) 8 of the fourth embodiment is similar to the refrigerant water-cooling section 8 of the second embodiment, and the same components as those of the second embodiment are denoted by the same reference numerals. The explanation is omitted.

[0119] Hereinafter, the refrigerant water cooling section (water cooling condenser) 8 will be described in detail mainly with reference to FIGS.

[0120] As shown in FIG. 16 to FIG. 18, a single notch that enters the longitudinal inner side of the tube 10 at both longitudinal ends of each tube 10 and at the center in the width direction of the tube 10 Part l ib is provided. The notch l ib has a semicircular arc shape. Beads 12a and 12b are projected at appropriate positions on the outer surfaces of the tubes 10 in the thickness direction (both flat surfaces). The bead portions 12a and 12b located at the same position on the flat surface are the bead portions 12a, The longitudinal direction of 12b is set in a different direction. The adjacent tubes 10 in the stacking direction are arranged at equal intervals by adjoining the bead portions 12a and 12b. The cooling water passes between the tubes 10 using this interval. The bead portions 12a and 12b of the tube 10 arranged on the outermost side are in contact with a bead portion 30 (shown in FIG. 17) protruding from the inner surface of the tank 5c. Thereby, the coolant cooling unit 8 is accommodated so as not to move in the left-right direction in the tank 5c.

[0121] Inside each tube 10, an in-tube flow path 13 extending along the longitudinal direction of the tube is formed. The tube internal flow passage 13 is open to both longitudinal end surfaces 11 a of the tube 10. Inner fins 14 are arranged in the tube internal flow passage 13.

[0122] The tank members constituting each of the tanks 20A and 20B are an outer tank member 21 disposed on the outer side in the longitudinal direction of the tube 10 with respect to the longitudinal end surface 1 la of each tube 10, and a tube from the outer tank member 21. An inner tank member 22 disposed on the inner side in the longitudinal direction, and a pair of blocking plates 23 disposed at both end positions of the cylindrical space formed by the outer tank member 21 and the inner tank member 22. It is configured.

[0123] Each outer tank member 21 is a flat plate material. The upper outer tank member 21 is in contact with the ceiling of the tank 5c, and the lower outer tank member 21 is in contact with the bottom surface of the tank 5c. Thereby, the coolant cooling unit 8 is accommodated so as not to move in the vertical direction in the tank 5c. A connector insertion hole 21a (shown in FIG. 18) is formed in the center of each outer tank member 21! /. An inlet-side connector 24 is attached to the connector insertion hole 21 a of one outer tank member 21, and an outlet-side connector 25 is attached to the connector insertion hole 21 a of the other outer tank member 21. The connectors 24 and 25 are projected outside the tank 5c of the sub radiator 5! /.

[0124] The caulking claw portions 21b are projected from appropriate positions on the periphery of the outer tank member 21, respectively. When the tanks 20A and 20B are assembled, the outer tank member 21 and the inner tank member 22 are temporarily assembled by crimping the crimping claws 21b.

[0125] The inner tank member 22 has peripheral flat portions on both sides that are in close contact with the peripheral edge of the outer tank member 21.

A force is also integrally formed with 22a and a bent portion 22b which is located between the peripheral flat portions 22a on both sides and is bent inward in a semicircular arc shape following the notch 1 lb of the tube 10. Inner tank In the member 22, a plurality of tube insertion holes 22c are formed at equal intervals. The end portions in the longitudinal direction of the tube 10 are inserted into the respective tube insertion holes 22c. Both end surfaces 11a in the longitudinal direction of the tube 10 inserted into the tube insertion hole 22c are in contact with the inner surface of the outer tank member 21. The inner tank member 22 is formed with a pair of closing plate insertion holes 22d at both side positions outside the plurality of tube insertion holes 22c.

[0126] Each closing plate 23 is inserted into a closing plate insertion hole 22d of the inner tank member 22, respectively. The insertion tip surface of each closing plate 23 is in contact with the inner surface of the outer tank member 21.

[0127] With the above configuration, in the tanks 20A and 20B, tank internal passages 26 are located inside the outer tank member 21 and the inner tank member 22, and both sides thereof are closed by the pair of closing plates 23. Is formed. That is, the tank inner passage 26 is formed in a partial region inside the longitudinal end surface 11a of the tube 10 with the inner surface of the outer tank member 21 as the outer surface of the tank inner passage 26. The tank passage 26 communicates with the tube passage 13 at the notch l ib of each tube 10.

[0128] Further, the portions of the refrigerant water cooling section 8 that are in contact with each other are fixed by brazing. Accordingly, between the longitudinal end of each tube 10 and each tank 20A, 20B, specifically, between the longitudinal end surface 11a of the tube 10 and the inner surface of the outer tank member 21, and The tube 10 and the inner surface of the tube insertion hole 22c of the inner tank member 22 are brazed.

Next, the arrangement structure of the inner fins 14 will be described. As shown in FIGS. 19 (a) and 19 (b), the inner fin 14 has a wave shape in the width direction. The inner fin 14 is formed in a dimension that is disposed only at an inner position further than the innermost position of the notch portion ib at both ends in the longitudinal direction of the tube 10. Both end surfaces of the inner fin 14 in the longitudinal direction are formed as straight cut surfaces 14a cut along the direction perpendicular to the longitudinal direction. This straight force surface 14a is in contact with a pair of left and right projections 12c projecting into the tube internal flow passage 13 of the tube 10, so that the inner fin 14 cannot move within the tube internal flow passage 13. Is contained. The pair of left and right projections 12c are elliptical in an oblique direction with respect to the straight force surface 14a of the inner fin 14. The flow of multiple channels and the entrance / exit of the shift are not blocked!

[0130] The main features of the heat exchanger (refrigerant water cooling unit) 8 of the fourth embodiment are listed below.

[0131] In the fourth embodiment, the tanks 20A, 20B have an outer tank member 21 disposed outside the longitudinal end surface 1 la of the tube 10, and the inner surface of the outer tank member 21 is the outer surface of the tank inner passage 26. As shown, an in-tank passage 26 is formed on the inner side in the longitudinal direction of the tube 10 from the longitudinal end surface 11a of the tube 10.

Accordingly, since the tank passage 26 is formed inside the longitudinal end surface 11a of the tube 10, the longitudinal dimension L6 of the tube 10 approaches the dimension of the installation width L7 of the refrigerant water cooling unit 8. In addition, the end region in the longitudinal direction of the tube 10 where the tank passage 26 is not formed becomes a heat exchange region. As described above, in the refrigerant water cooling section 8 including the pair of tanks 20A and 20B and the plurality of tubes 10, the heat exchange efficiency can be improved without changing the overall size.

[0133] In the fourth embodiment, the outer tank member 21 is in contact with the longitudinal end surface 11a of the tube 10. Therefore, the dimension L6 in the longitudinal direction of the tube 10 can be made closer to the dimension of the installation width L7 of the refrigerant water cooling unit 8. Therefore, the heat exchange efficiency is further improved. Specifically, in a region where the tank passage 26 is not formed at the longitudinal end of the tube 10, the dimension L6 is slightly shorter than the installation width L7 of the refrigerant water cooling unit 8, as shown in FIG. Therefore, the effective heat exchange area of the tube 10 is greatly expanded compared to the conventional case.

[0134] In the fourth embodiment, at both ends in the longitudinal direction of the tube 10, the notches l ib that enter the inside from the longitudinal end surface 11a of the tube 10 are respectively located at the center in the width direction of the tube 10. A tank passage 26 is formed using 1 lb of the notch!

Accordingly, since the notch l ib is provided between both ends of the tube 10 in the width direction, the in-tank passage 26 can be easily formed using the notch l ib. Further, since the notch l ib is provided between both ends of the tube 10 in the width direction, the rigidity of the tube 10 does not extremely decrease.

[0136] In the fourth embodiment, since the notch l ib formed at the longitudinal end of each tube 10 is single, a single tank internal passage 26 can be formed. There may be a plurality of notches l ib.

[0137] In the fourth embodiment, the notch l ib has a substantially semicircular arc shape. Therefore, the notch l ib As a result, the outer surface of the tanks 20A and 20B on the tube 10 side is almost semicircular, so the cooling water flowing in the vicinity of the tanks 20A and 20B and outside the tubes 10 is indicated by the arrow a in FIG. It flows smoothly. Therefore, it contributes to improvement of heat exchange. Further, since the tank passage 26 is also semicircular, the tanks 20A and 20B have a shape excellent in the pressure resistance of the refrigerant flowing through the tank passage 26.

[0138] In the fourth embodiment, the tanks 20A and 20B are provided with a plurality of tube insertion holes at intervals.

22c, and both end portions in the longitudinal direction of the respective tubes 10 are inserted into the respective tube insertion holes 22c. Therefore, by inserting the longitudinal ends of the tubes 10 into the tube insertion holes 22c of the tanks 20A and 20B, a plurality of tubes 10 can be arranged at a predetermined interval. Therefore, the tanks 20A and 20B and the tubes 10 Is easy to assemble.

[0139] In the fourth embodiment, each of the tanks 20A, 20B is arranged inside the outer tank member 21 in addition to the outer tank member 21, and a plurality of tube bottles into which the longitudinal ends of the tubes 10 enter. An inner tank member 22 having an inlet hole 22c is provided, and an in-tank passage 26 is formed inside the outer tank member 21 and the inner tank member 22. Therefore, the tanks 20A and 20B can be formed by assembling the outer tank member 21 and the inner tank member 22.

Yes

[0140] In the fourth embodiment, the inner tank member 22 is located between the peripheral flat portions 22a on both sides that are in close contact with the outer tank member 21 and the peripheral flat portions 22a on both sides, and the notch portion l of the tube 10 is provided. and a bent portion 22b that bends inward following ib. Therefore, by using the tube 10 having the notch l ib at the longitudinal end, the liquid-tight tank passage 26 can be easily formed by the outer tank member 21, the inner tank member 22, and the pair of closing plates 23. . Therefore, the refrigerant water cooling unit 8 can be manufactured without increasing the number of parts compared to the conventional example.

[0141] In the fourth embodiment, the end portions of the tubes 10 in the longitudinal direction and the locations where the tanks 20A and 20B abut each other are brazed. Accordingly, the portions of the tubes 10 and the tanks 20A, 20B that are in contact with each other are firmly fixed in a liquid-tight manner. Further, since the longitudinal end of each tube 10 is brazed to both the inner tank member 22 and the outer tank member 21, the fixing strength between each tube 10 and the tank 20 is improved, and as a result, the coolant water cooling is performed. Strength of part 8 is improved To do.

[0142] (Modification of Fourth Embodiment)

Fig. 20 shows the structure of the inner fin itself and a modified example of its arrangement. Fig. 20 (a) is a cross-sectional view of the main part showing the arrangement of the inner fin, and Fig. 20 (b) is a front view of the main part of the inner fin. It is.

As shown in FIGS. 20 (a) and 20 (b), the inner fin 15 has a wave shape in the width direction as in the fourth embodiment. However, the inner fin 15 is formed to have substantially the same length as the tube 10 unlike the fourth embodiment. Then, both end portions in the longitudinal direction of the inner fin 15 are formed on a V-shaped cut surface 15a that gradually cuts inwardly toward the center from both ends in the width direction. The left and right ends of the V-shaped cut surface 15 a abut against the outer tank member 21, so that the inner fin 15 cannot move in the tube flow path 13. Thus, the V-shaped cut surface 15a is located outside the tank passage 26. In other words, the inner fin 15 is not arranged near the entrance entering the tube internal flow passage 13 from the tank internal passage 26 by the V-shaped cut surface 15a! /.

[0144] As shown by the arrows in FIG. 20 (a), the refrigerant entering the tubes 10 from the tank passage 26 smoothly flows into the tubes 10 without being interfered by the inner fins 15 in the flow direction. There is no refrigerant flow density in the width direction of the tube internal flow passage 13. Therefore, in this modified example, as in the fourth embodiment, the inner fin 15 can be positioned without providing the tube 10 with the protruding portion protruding toward the tube internal flow passage 13, and the heat exchange efficiency can be improved. Can be achieved.

[0145] (Fifth embodiment)

FIGS. 21 to 25 show a fifth embodiment of the present invention, FIG. 21 is a front view of a refrigerant water cooling unit installed in the tank part of the sub radiator, and FIG. 22 is a refrigerant water cooling unit installed in the tank part of the sub radiator. FIG. 23 is an exploded perspective view of the main part of the refrigerant water cooling unit, FIG. 24 is a cross-sectional view taken along line AA in FIG. 23, and FIG. 25 is a cross-sectional view taken along line BB in FIG.

[0146] The heat exchanger according to the fifth embodiment is applied to the refrigerant water cooling unit 8 as in the fourth embodiment, and the same components as those in the fourth embodiment are denoted by the same reference numerals and the same reference numerals are given to the same components. The explanation is omitted and only the different components are explained. [0147] As shown in Figs. 21 to 230, both end portions in the longitudinal direction of each tube 10 are formed in the widened portion 16 in which all end portions including the cutout portion l ib are wider than other portions, respectively. ing. The widened portions 16 at both ends of the adjacent tubes 10 are in close contact with each other and are joined in a liquid-tight manner by brazing as described below.

[0148] The tanks 20A and 20B are composed of an outer tank member 21, a tube converging member 22A, and a pair of closed plates 23. Similar to the inner tank member 22 of the fourth embodiment, the tube converging member 22A has the same contour shape including the peripheral flat portion 22a on both sides and the bent portion 22b at the center thereof. In contrast, a single tube converging hole 27 is formed in which the ends of all the tubes 10 enter. The ends of all the tubes 10 are inserted into the single tube converging hole 27. Thereby, the end portions of the plurality of tubes 10 are bundled by the tube bundling member 22A. Further, plate locking grooves 22e are formed at both ends of the bent portion 22b of the tube converging member 22A.

Yes

[0149] Each closing plate 23 has a locking projection 23a on an arcuate surface. Each closing plate 23 is disposed at both ends of the outer tank member 21 and the tube converging member 22A in a state where the locking projection 23a is locked in the plate locking groove 22e.

[0150] With the above configuration, the tanks 20A and 20B have tanks surrounded by the outer tank member 21, the tube converging member 22A, and the plurality of tubes 10, and closed on both sides by the pair of closing plates 23. A passage 26 is formed. That is, the tank inner passage 26 is formed in a partial region inside the longitudinal end surface 11a of the tube 10 with the inner surface of the outer tank member 21 being the outer surface of the tank inner passage 26. As shown in FIGS. 24 and 25, the in-tank passage 26 communicates with the in-tube passage 13 at the notch portion ib of each tube 10.

[0151] Further, the portions of the refrigerant water cooling unit 8 that are in contact with each other are fixed by brazing. Accordingly, between the tubes 10 and the tanks 20A, 20B, the portions of the tubes 10 and the inner surfaces of the tube converging holes 27 of the tube collecting member 22A that are in contact with each other are brazed. As described above, the widened portions 16 that are in contact with each other are brazed between the adjacent tubes 10. [0152] Since the other configuration is the same as that of the fourth embodiment, description thereof will be omitted to avoid redundant description. The same components in the drawings are denoted by the same reference numerals for clarification.

In the fifth embodiment, as in the fifth embodiment, the tank internal passage 26 is formed inside the longitudinal end face 1 la of the tube 10, so that the longitudinal dimension L 6 of the tube 10 is reduced to the refrigerant. Dimension of installation width of water cooling part 8 Can be made long so as to approach L7. In addition, the end region of the tube 10 where the tank passage 26 is not formed becomes a heat exchange region. As described above, in the refrigerant water cooling section 8 including the pair of tanks 20A and 20B and the plurality of tubes 10, the heat exchange efficiency can be improved without changing the overall size.

[0154] Also in the fifth embodiment, the outer tank member 21 is in contact with the longitudinal end surface 11a of the tube 10. Therefore, since the length L6 of the tube 10 in the longitudinal direction can be made as long as possible as close as possible to the width L7 of the installation width of the refrigerant water cooling section 8, the heat exchange efficiency is further improved. Specifically, in the region of the tube 10 where the tank passage 26 is not formed, as shown in FIG. 21, the dimension L6 slightly shorter than the installation width dimension L7 of the refrigerant water cooling section 8 is the actual length of the tube 10. Since the length is L6, the effective heat exchange area of the tube 10 is greatly expanded compared to the conventional case.

[0155] In the fifth embodiment, the end portions on both sides in the longitudinal direction of the tube 10 are formed in the widened portion 16 that is wider than the other portions, and the widened portions 16 of both adjacent tubes 10 are liquid-tight. The tanks 20A and 20B are formed by the outer tank member 21 and the widened portions 16 of the plurality of tubes 10. Therefore, since the plurality of tubes 10 can be arranged at equal intervals by arranging the plurality of tubes 10 in a state where the widened portions 16 thereof are in close contact with each other, the assembling property of the plurality of tubes 10 is excellent.

[0156] In the fifth embodiment, the end portions on both sides in the longitudinal direction of each tube 10 are provided with notches 1 lb that enter the inside from the longitudinal end surface 11a of the tube 10 at the center position from the end in the width direction of the tube 10. Each of the tanks 20A and 20B has a single unit in addition to the outer tank member 21. The tube converging member 22A having the tube converging hole 27 is formed, and the widened portions 16 of the plurality of tubes 10 that are liquid-tightly joined to the tube converging hole 27 of the tube converging member 22A are collectively inserted. The end of multiple tubes 10 by the tube converging member 22A The parts are united. Therefore, the plurality of tubes 10 can be firmly fixed to the outer tank member 21 by the tube converging member 22A. Therefore, the fixing strength between the tubes 10 and the tanks 20A and 20B is improved, and the strength of the heat exchanger is improved.

[0157] Also in the fifth embodiment, the cutout portion ib has a substantially semicircular arc shape as in the fourth embodiment. Accordingly, the outer surface of the tanks 20A and 20B on the tube 10 side is almost semicircular due to the notch l ib, so the cooling water flowing outside the tanks 20A and 20B and outside the tube 10 is Flows smoothly as indicated by the arrow b in Fig. 21. Therefore, it contributes to the improvement of heat exchange. Further, since the tank passage 26 also has a semicircular arc shape, the tanks 20A and 20B have a shape excellent in pressure resistance of the refrigerant flowing through the tank passage 26.

[0158] In the fifth embodiment, not only the end portions of each tube 10 and the pair of tanks 20A, 20B are in contact with each other, but also the widened portions 16 of the adjacent tubes 10 that are in contact with each other are brazed. ing. Therefore, it is possible to reliably fix the widened portions 16 of the tube 10 and secure the liquid tightness of the gaps by the brazing operation.

In this fifth embodiment, the configuration and arrangement of the inner fins 14 may adopt a modification of the fourth embodiment.

[0160] In the fourth and fifth embodiments, the case where the heat exchanger of the present invention is applied to the refrigerant water cooling unit 8 is shown. However, the refrigerant air cooling unit 7 (air cooling type condenser) and the internal cooling water flow. It can also be applied to radiators and other heat exchangers.

Claims

The scope of the claims

[1] A core portion in which a plurality of cooling water flat tubes (5a) having an internal passage for cooling water are stacked in multiple stages, and a cooling water tank (5c) into which cooling water that has passed through the core portion flows. And a cooling water heat exchanger (5) equipped with

Built in the cooling water tank (5c) of the cooling water heat exchanger (5), heat is passed between the refrigerant and the cooling water in the cooling water tank (5c) by allowing the refrigerant to flow inside. A composite heat exchanger (1) having a refrigerant water cooling section (8) to be exchanged,

The refrigerant water cooling section (8)

A core portion in which a refrigerant flat tube (10) having an internal passage for refrigerant is laminated in a plurality of stages;

The refrigerant flat tube (10) has an in-tank passage (26) extending in the stacking direction, and one open end of the refrigerant flat tube (10) in the longitudinal direction is inserted. A first refrigerant tank (20A) in communication with the internal passage;

A tank internal passage (26) extending in the stacking direction of the refrigerant flat tube (10), and the other open end of the refrigerant flat tube (10) in the longitudinal direction is inserted; A second refrigerant tank (20B) in communication with

[2] A composite heat exchanger (1) according to claim 1,

Since the outline of the cross-sectional shape of the tank passage (26) has an arc shape, the width (L1) of the tank passage (26) is set smaller than the width (L2) of the refrigerant flat tube. .

[3] A composite heat exchanger (1) according to claim 1,

One end of the flat tube (10) in the longitudinal direction is abutted against the inner surface of the first refrigerant tank (20A), and the other end in the longitudinal direction is abutted against the inner surface of the second refrigerant tank (20B). It has been applied.

[4] The composite heat exchanger (1) according to claim 1, The first refrigerant tank (20A) is joined to one end in the longitudinal direction of the cooling water tank (5c) in the cooling water tank (5c),

The second refrigerant tank (20B) is joined to the other longitudinal end of the cooling water tank (5c) in the cooling water tank (5c).

[5] The composite heat exchanger (1) according to claim 1,

The refrigerant discharged from the compressor of the refrigeration cycle flows into the refrigerant water cooling section (8).

[6] The composite heat exchanger (1) according to claim 1,

It further includes a condenser (6) for the refrigeration cycle,

The capacitor (6)

The refrigerant water cooling section (8) for cooling the refrigerant flowing through the condenser (6) with the cooling water in the cooling water tank (5c) of the cooling water heat exchanger (5);

A refrigerant air-cooling section (7) for cooling the refrigerant flowing through the condenser (6) with air.

[7] The composite heat exchanger (1) according to claim 6,

The refrigerant flowing through the condenser (6) flows in the order of the refrigerant water cooling section (8) and the refrigerant air cooling section (7).

[8] The composite heat exchanger (1) according to claim 6,

The cooling water tank (5c) is joined to the refrigerant tank (7c) of the refrigerant air cooling section (7).

[9] A width (L3) of the core portion of the coolant water cooling section (8) and a width (L4) of the cooling water flat tube (5a) along the stacking direction of the coolant flat tube (10) is there.

[10] The composite heat exchanger according to claim 1,

The cooling water heat exchanger (5) cools the electric drive section (4).

[11] A first heat exchanger (5) for dissipating heat of the first heating element through the first fluid by circulating the first fluid between the first heating element and the first heating element, A first heat exchanger (5) having a first fluid tank (5c) through which the first fluid flows;

A second heat exchanger (7) for dissipating the heat of the second heating element through the second fluid by circulating the second fluid between the second heating element and the second heating element; Forms a part of a second fluid line for circulating the second fluid between the second heating element and the second heat exchanger (7), and is built in the first fluid tank (5c) A second fluid cooling section (8) for exchanging heat between the first fluid and the second fluid in the first fluid tank (5c),

A combined heat exchanger (1) comprising:

The second fluid cooling section (8)

A core portion in which a plurality of flat tubes (10) each having an internal passage for the second fluid are stacked in multiple stages, and a tank internal passage (26) extending in the stacking direction of the flat tubes (10), One open end of the flat tube (10) is inserted and communicated with the second fluid internal passage, and the upstream second fluid tank (20A) supplied to each of the flat tubes (10). )When,

A tank internal passage (26) extending in the laminating direction of the flat tube (10) is provided therein, and the other open end of the flat tube (10) is inserted into the second fluid internal passage. A second fluid tank (20B) on the downstream side into which the second fluid flowing through the flat tube (10) flows, and

Have

In the second fluid tank (20A) on the upstream side and the second fluid tank (20B) on the downstream side, the width (L1) of the passage (26) in the tank is smaller than the width (L2) of the flat tube. ! /

[12] The composite heat exchanger (1) according to claim 11,

Since the outline of the cross-sectional shape of the passage (26) in the tank has an arc shape, the width (L1) of the passage (26) in the tank is set smaller than the width (L2) of the flat tube! /,

[13] The composite heat exchanger (1) according to claim 11,

The first heat exchanger (5) includes a first fluid flat tube (5a) that exchanges heat between the first fluid and air by circulating the first fluid therein, The first fluid tank (5c) is provided downstream of the first fluid flat tube (5a);

The second fluid cooling section (8) is upstream of the second heat exchanger (7) in the second fluid line. [14] A first heat exchanger (5) for dissipating heat of the first heating element through the first fluid by circulating the first fluid between the first heating element and the first heating element. A first heat exchanger (5) having a first fluid tank (5c) through which one fluid flows;

A second heat exchanger (7) for dissipating the heat of the second heating element through the second fluid by circulating the second fluid between the second heating element and the second heating element;

The second heating element and the second heat exchanger (7) are connected to form a part of the second fluid line for circulating the second fluid and attached to the first fluid tank (5c). And a second fluid cooling section that exchanges heat between the first fluid from the first fluid tank (5c) and the second fluid by being connected to the first fluid tank (5c). 70), and a combined heat exchanger comprising:

The second fluid cooling section (70) includes a first plate and a second plate (76, 77) having a flat plate shape in which the inflow direction of the first fluid from the first fluid tank (5c) and the plate surface are orthogonal to each other. Are alternately stacked so that the first plate and the second plate are separated from each other and the peripheral edge thereof is liquid-tightly joined, and the first fluid flows in the plate stacking direction. The passages (78) and the second passages (79) through which the first fluid flows are alternately provided.

[15] The composite heat exchanger (1) according to claim 14,

The first heat exchanger (5) includes a first fluid flat tube (5a) that exchanges heat between the first fluid and air by circulating the first fluid therein.

The second passage (79) of the second fluid cooling section (70) is connected to the downstream side of the first fluid flat tube (5a) via the first fluid tank (5c).

The first passage (78) of the second fluid cooling section (70) is upstream of the second heat exchanger (7) in the second fluid line.

[16] The composite heat exchanger (1) according to claim 14,

The first fluid tank (5c) is formed in a box shape with one side surface formed as an opening, and the periphery of the opening of the first fluid tank (5c) and the periphery of the second fluid cooling part (70) And the opening is closed.

[17] The composite heat exchanger (1) according to claim 14,

The second fluid cooling part (70) is configured such that the first fluid and the second fluid face each other. It flows in the direction.

[18] The composite heat exchanger (1) according to claim 14,

The second fluid cooling section (70) has an inner fin (80) disposed in the first passage (78).

[19] The composite heat exchanger (1) according to claim 14,

The first fluid is cooling water for cooling the electronic component (4) for controlling the electric motor for the vehicle,

The second fluid is a refrigerant circulating in the refrigeration cycle of the air conditioning system.

[20] A core portion in which a plurality of cooling water flat tubes (5a) having an internal passage for cooling water are stacked in multiple stages, and a cooling water tank (5c) into which the cooling water that has passed through the core portion flows. And a cooling water heat exchanger (5) equipped with

The refrigerant water cooling section (8)

A tank internal passage (26) extending in the stacking direction of the refrigerant flat tube (10), and the other open end of the refrigerant flat tube (10) in the longitudinal direction is inserted; A second refrigerant tank (20B) communicating with the

Have

The tank members constituting the refrigerant tanks (20A, 20B) are outer tanks arranged on the outer side in the longitudinal direction of the tube (10) from the longitudinal end surfaces (11a) of the plurality of refrigerant flat tubes (10). Having a member (21),

The inner surface of the outer tank member (21) is the outer surface of the tank internal passage (26), The tank passage (26) is formed on the inner side in the longitudinal direction of the tube (10) from the longitudinal end face (1 la) of the tube (10).

[21] heat exchanger (8),

A plurality of tubes (10) each having a tube inflow passage (13) therein, and a tank passage disposed at both ends in the longitudinal direction of the tube (10) and connected to the tube inflow passage (13) (26) and a pair of tanks (20A, 20B), and tank members constituting the tanks (20A, 20B) are arranged in the longitudinal direction end faces (1 la) of the tubes (10). An outer tank member (21) disposed on the outside in the longitudinal direction of the tube (10);

The inner surface of the outer tank member (21) serves as the outer surface of the tank passage (26), and the tank passage (inside the longitudinal end surface (1 la) of the tube (10) in the longitudinal direction of the tube (10) ( 26) is formed!

[22] The heat exchanger (8) according to claim 21,

A longitudinal end surface (11a) of the tube (10) is in contact with the outer tank member (21).

[23] The heat exchanger (8) according to claim 21,

The tank internal passage (26) is formed between both ends of the tube (10) in the width direction.

[24] A heat exchanger (8) according to claim 23,

At both ends in the longitudinal direction of the tube (10), at least one notch (l ib) entering the inner side from the longitudinal end surface (11a) of the tube (10) at the center in the width direction of the tube (10). The tank passage (26) is formed using the notch (l ib).

[25] A heat exchanger (8) according to claim 24,

The heat exchanger (8) according to claim 4, wherein only one notch (l ib) is provided at a longitudinal end of each tube (10).

The notch (l ib) has a substantially semicircular arc shape. [27] The heat exchanger (8) according to claim 21,

The tank (20A, 20B) includes a tube insertion hole (22c) into which the longitudinal end of the tube (10) is inserted.

[28] A heat exchanger (8) according to claim 21,

The tanks (20A, 20B) include, in addition to the outer tank member (21), an inner tank member (22) disposed on the inner side in the longitudinal direction of the tube from the outer tank member (21). An inner tank member (22) having a tube insertion hole (22c) into which the longitudinal end of 10) enters;

The tank internal passage (26) is formed on the inner side surrounded by the outer tank member (21) and the inner tank member (22).

[29] A heat exchanger (8) according to claim 28,

The inner tank member (22) is positioned between the peripheral flat portions (22a) on both sides that are in close contact with the outer tank member (21) and the peripheral flat portions (22a) on both sides. And a bent portion (22b) that bends along the notch (1 lb).

[30] A heat exchanger (8) according to claim 21,

Both ends in the longitudinal direction of the tube (10) are configured as widened portions (16) whose thickness is larger than the central side in the longitudinal direction of the tube (10), and the tubes (10) adjacent to each other in the stacking direction are configured. The widened portions (16) are joined together.

[31] A heat exchanger (8) according to claim 21,

Both ends in the longitudinal direction of the tube (10) enter the inner side in the longitudinal direction of the tube (10) from the longitudinal end surface (1 la) of the tube (10) at the center in the width direction of the tube (10). Has a notch (1 lb)

Both end portions in the longitudinal direction of the tube (10) are configured as widened portions (16) whose thickness is larger than the longitudinal center side of the tube (10),

The widened portions (16) of the tubes (10) adjacent to each other in the stacking direction are joined together, and the tank member constituting the tank (20A) includes the outer tank member (21) and the outer tank member (21). A single tube housing that is disposed inside the tube in the longitudinal direction of the tube and is received by bundling the longitudinal ends of the tubes (10) stacked in multiple stages. A tube converging member (22A) having a bundle hole (27).

[32] A heat exchanger (8) according to claim 11,

A portion where the longitudinal end of the tube (10) and the tank (20A, 20B) contact each other is brazed.

[33] A heat exchanger (8) according to claim 30 or 31,

The said tube (10) widening part (16) adjacent to the lamination direction is brazed.

[34] The heat exchanger (8) according to claim 21,

Inner fins (14, 15) disposed in the tube internal flow passage (13) of the tube (10) are further provided.

[35] A heat exchanger (8) according to claim 34,

The inner fin (14) is arranged on the inner side in the longitudinal direction of the tube (10) with respect to the passages (26) in the tank formed at both longitudinal ends of the tube (10).

[36] A heat exchanger (8) according to claim 34,

The tube (10) includes a protrusion (12c) that protrudes into the tube internal flow passage (13) and restricts movement of the inner fin (14).

[37] A heat exchanger (8) according to claim 34,

The longitudinal ends of the tube (10) are notched into the central portion in the width direction of the tube (10) and enter the inside of the tube (10) in the longitudinal direction from the longitudinal end surface (11a) of the tube (10). (L ib)

Both ends of the inner fin (15) in the longitudinal direction are gradually cut into the inner side in the longitudinal direction of the inner fin (15) according to the force in the widthwise direction of the inner fin (15), the direction force toward the center in the width direction. With cut surface (15a)

An end in the width direction of the V-shaped cut surface (15) contacts the outer tank member (21), and the V-shaped cut surface (15) is located outside the tank internal passage (26).