JPH11264675A - Juxtaposed integral heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To eliminate adverse effect of on the heat exchanging performance of each heat exchanger by suppressing heat transfer between adjacent fins in adjacent heat exchangers in a structure where a plurality of heat exchangers having alternating fins and tubes are combined integrally. SOLUTION: Fins 4, 8 are formed of different members for a condenser 5 and a radiator 9 brazed integrally while facing the heat exchanging sections each other. Tubes 3, 7 of respective heat exchangers are made of a material clad with a brazing material 31 while the fins 4, 8 of adjacent heat exchangers are made of a bare material clad with no brazing material. The adjacent fins 4, 8 simply touch each other even when they are abutted each other thus suppressing the quantity of heat being transferred from the fin 4 of the radiator 9 to the fin of the condenser 5. Area at the heat exchanging section of the condenser 5 may be different from that of the radiator 9.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a conventional heat exchanger in which a plurality of heat exchangers are arranged one behind the other in the airflow direction, and adjacent heat exchangers are integrally connected such that respective heat exchange portions face each other. The present invention relates to an integrated heat exchanger.

[0002]

2. Description of the Related Art In recent years, there has been a demand for integrating a plurality of heat exchangers (for example, a condenser and a radiator) for different purposes due to restrictions on the space in a vehicle. As a method of integrating multiple heat exchangers, there is a method of integrating fins, tubes, tanks, etc. with adjacent heat exchangers, or a separate connection after temporarily assembling each heat exchanger separately There is a method of connecting each heat exchanger via a member.

However, for example, when a condenser and a radiator are integrated, thermal interference between the two heat exchangers (the heat of one heat exchanger reduces the heat of the other) due to the difference in the operating temperature range between the condenser and the radiator. Is transmitted to the heat exchanger, and the original heat exchange performance may be impaired).

As means for suppressing this thermal interference,
The configuration disclosed in Japanese Utility Model Publication No. 6-45155 is considered as an example, and the configuration described in Japanese Utility Model Application Laid-Open No. 1-88163 is considered as an example.

In the former, each of a condenser and a radiator is constituted by a pair of headers, a plurality of tubes communicating between the headers, and fins interposed between the tubes. Are formed separately so that the fins can be shared by both heat exchangers.A slit is formed in the common fin between the condenser and the radiator, and one heat fin is formed. The transfer of heat from the exchange section (radiator) to the other heat exchanger (condenser) via fins is suppressed as much as possible. In the latter, different types of heat exchangers are arranged at predetermined intervals, and are integrally connected with a side plate (reinforce).

[0006]

However, in the structure in which the fins are integrated between the adjacent heat exchangers as in the former case, the strength of the portions where the slits are formed is reduced. The slit cannot be made extremely large in height, and it is necessary to take great care not to deform the fins in the assembly before brazing.

[0007] Further, in the configuration in which a predetermined gap is formed between the heat exchange sections as in the latter, the fins of the adjacent heat exchangers also need to face each other at a predetermined interval. Extra jigs such as spacers need to be attached, and the number of man-hours is increased, which may lower production efficiency.

Therefore, according to the present invention, when a plurality of heat exchangers are integrated, the heat transfer between the heat exchangers of adjacent heat exchangers is reduced, and the heat exchange performance of each heat exchanger due to the heat transfer is reduced. It is an object of the present invention to provide a side-by-side integrated heat exchanger with reduced influence on fins, to eliminate concerns about fin strength, and to improve production efficiency by eliminating spacers.

In order to achieve the above object, the present applicant has
Adjacent fins of heat exchanger are composed of separate members, and adjacent fins are joined out of phase (brazing)
In addition, a configuration in which the heat transfer is suppressed by reducing the bonding area between the fins has been previously proposed (Japanese Patent Application No. 9-320).
388), and the effect of suppressing heat transfer has been confirmed experimentally. The present invention is based on the finding of the present inventors that, unlike such a configuration, the relationship between the fin material and the tube material constituting each heat exchanger affects the heat transfer between adjacent fins. The feature is that the same problem is to be realized by trying an approach from the relationship between the fin material and the tube material.

[0010]

That is, a parallel-integrated heat exchanger according to the present invention has a plurality of heat exchangers having a heat exchange portion formed by alternately stacking fins and tubes. Arranged in front and back, adjacent heat exchangers are integrally connected to each other with the heat exchange portions facing each other,
The fins of each heat exchanger are formed with separate members,
The tube is made of a clad material with a brazing material clad, and each of the fins is made of a bare material with no brazing material clad (claim 1).

In such a configuration, it is planned that the fins of the adjacent heat exchange portions may come into contact with each other at the time of assembling or brazing, and even in the case of contact, the fins are clad with a brazing material. Since the fins are not in contact, the contact portions between the fins are not brazed. In other words, the aim of using fins as bare material is to avoid a configuration in which adjacent fins are joined together to increase the amount of heat transfer, and that even if the fins abut, they are just in contact To reduce the amount of heat transfer. Therefore, adjacent fins may be shifted in phase or may have the same phase.

The plurality of heat exchangers may have the same use or different uses. However, in the present invention, in particular, in the present invention, a plurality of heat exchangers having different temperature ranges during use are used. This is effective when integrating the heat exchangers. In addition, adjacent heat exchangers are joined together with their heat exchange portions facing each other.
Even if side plates are attached to the outermost side of each heat exchange part and adjacent heat exchangers are joined by brazing the side plates to each other, the outermost side plate is shared by the adjacent heat exchangers The heat exchanger may be formed with one plate so as to be able to connect adjacent heat exchangers with this side plate.

Further, even if the plurality of heat exchangers are joined by abutting the headers of adjacent heat exchangers and joining the header portions, the heat exchangers can be joined by joining only the fins of the facing heat exchangers. They may be combined. Alternatively, adjacent heat exchangers may be connected by the above combination.

As a more specific parallel-integrated heat exchanger, a heat exchange portion is constituted by corrugated fins and a plurality of tubes stacked via the fins, and a stacking direction of the plurality of tubes is defined. And first and second heat exchangers provided with headers extending to the respective tubes and communicating with the tubes, wherein the first and second heat exchangers connect the respective heat exchangers to the tubes. Assuming a configuration in which the fins of the first heat exchanger and the fins of the second heat exchanger are formed as separate members, and the tube is formed by assuming a configuration in which the fins of the first heat exchanger and the fins of the second heat exchanger are coupled in the same stacking direction. It is preferable that the brazing material is made of a clad material clad, and each of the fins is made of a bare material that is not clad with the brazing material.

From the viewpoint of reducing the amount of heat transfer, it is preferable that the fins of the heat exchangers adjacent to each other between the heat exchange sections facing each other are provided out of phase. Especially,
It is practical to form the fins of the first heat exchanger and the fins of the second heat exchanger in the same shape and shift the phases of the adjacent fins by ピ ッ チ pitch. The term "1/2 pitch" as used herein does not exclude the case where there is a portion that does not become exactly 1/2 pitch due to variations in the manufacturing process, and such a case should be included in the present invention. It is. According to such a configuration, the fins of each heat exchanger can be formed simultaneously on the same production line.

In order to minimize the number of contact points between adjacent fins between opposing heat exchange sections,
Instead of shifting the phases of the fins, the adjacent fins of each heat exchanger may be formed with different pitches (claim 5).

The fins may be corrugated, and the tube constituting at least one heat exchanger may be an inner fin tube formed by inserting fins inside an electric resistance welded tube. It may be a tube formed by roll forming with a sheet (claims 6 and 7).

Therefore, with the above-described configuration, in each of the heat exchangers, the heat of the fluid flowing in the tubes is transmitted to the fins, whereby the fluid in the tubes exchanges heat with the fluid passing between the fins. However, since the fins of each heat exchanger are made of bare material, even if the fins abut each other, they only come into contact with each other. The contact area and the degree of close contact are not ensured as much as a similar configuration reliably joined by the brazing material, and as a result, the amount of heat transfer between the fins can be reduced.

The adjacent heat exchangers described above may have the same area or may have different areas. For example,
Even if the lengths of the first heat exchanger and the second heat exchanger in the stacking direction are different (claim 8), the stacking direction of the first heat exchanger and the second heat exchanger is different. May be made different in the length of the tube extending in the direction perpendicular to the first direction (Claim 9). Further, by combining these, the first heat exchanger and the second heat exchanger are stacked in the stacking direction. May be different from the length of the tube perpendicular to the length of the tube (claim 10).

[0020]

Embodiments of the present invention will be described below with reference to the drawings. 1 to 3, the parallel-integrated heat exchanger 1 is entirely made of an aluminum alloy, and includes a pair of headers 2a and 2b and a pair of headers 2a and 2b.
(a) and (b), a capacitor 5 having a plurality of flat tubes 3 and corrugated fins 4 inserted and joined between the tubes, and a pair of headers 6
a, 6b, a plurality of flat tubes 7 communicating the pair of headers, and a radiator 9 having corrugated fins 8 inserted and joined between the tubes. It is configured. Each of the heat exchangers constitutes a heat exchange section for exchanging heat between a fluid flowing through the tubes and air passing between the fins by the plurality of tubes 3, 7 and the fins 4, 8. The parts are opposed to each other and are integrally assembled.

The tube 3 of the condenser 5 is shown in FIG.
As shown in FIG. 1, for example, an inner fin tube in which a fin 3b is inserted into an electric resistance welded tube 3a is used. The headers 2a and 2b of the capacitor 5 are
Both ends of the cylindrical member 10 are closed by lids 11, and a plurality of tube insertion holes 12 for inserting the tubes 3 are formed in the peripheral wall of the cylindrical member 10. , 15b, 15c to define a plurality of flow chambers. An inlet portion 13 through which the refrigerant flows is provided at a portion of the header constituting the most upstream flow passage chamber, and an outlet portion 14 through which the refrigerant flows out is provided at the header portion constituting the most downstream flow passage chamber. Is provided.

In the configuration example shown in FIG. 1, one header 2a is defined by three partition walls 15a and 15b in three flow path chambers, and the other header 2b is formed by one partition wall 15a.
c, the two flow path chambers are defined, and one header 2a is provided with an inlet portion 13 and an outlet portion 14;
The refrigerant that has entered from the header is reciprocated twice between the headers, and
It flows out from

On the other hand, the tube 7 of the radiator 9
Is formed by a flat tube whose interior is not partitioned. The headers 6 a and 6 b of the radiator 9 are provided between a first header member 16 having a U-shaped cross section in which a tube insertion hole for inserting the tube 7 is formed, and a side wall portion of the first header member 16. The first header member 16 and the second header member 17 forming the peripheral wall of the header 6 together with the first header member 16 constitute a tubular body having a rectangular cross section, and both ends of the tubular body are closed by closing plates 18. It is configured.

The closing plate 18 is formed of a flat plate formed in a rectangular shape according to the cross-sectional shape of the header, and has projections formed on two opposing sides.
And fitted into the opening of the tubular body by fitting into a fitting hole 19 formed in the header member 17.

A locking groove 22 is formed in the second header member 17 by bending both side edges into a U-shape so as to swell, and the locking groove 22 is formed in the side wall of the first header member 16. The header members 16 and 17 are joined to each other by fitting the ends. The joint portion between the first header member 16 and the second header member 17 is located at a position away from the portion to which the tube 7 is joined, and is located outside the portion of the capacitor 5 facing the header 2a. .

One header 6b of the radiator 9 is provided with an inlet 26 into which a fluid flows, and the other header 6a
Is provided with an outlet portion 27 through which a fluid flows out. In this example, the inside of both headers 6a and 6b is not partitioned, and the fluid that has entered through the inlet portion 26 is supplied to one header 6a.
b to the other header 6a via the entire tube 7, and then flows out from the outlet 27.

Further, side plates 20 are attached to the outer sides of the laminated tubes 3 and 7 (upper and lower ends of the heat exchange portion in FIG. 1A) via fins 4 and 8, and the condenser 5 and the radiator 9 is integrally connected with the side plate 20. The side plate 20 is formed of, for example, a single plate shared by both heat exchangers, and a ventilation hole 21 is formed on a surface of the side plate 20 at a portion facing between the condenser 5 and the radiator 9. .

At least one ventilation hole 21 is formed as an elongated hole extending in the longitudinal direction of the side plate 20 and communicates with the outside between the condenser 5 and the radiator 9. To prevent the relatively high temperature air from stagnating between the condenser 5 disposed on the downstream side and the radiator 9 disposed on the downstream side, thereby lowering the heat radiation effect of the condenser 5 and flowing through the ventilation hole 21. It is provided for the purpose of, for example, directly guiding low-temperature air to the radiator 9 to promote the heat radiation action of the radiator 9.

The tubes 3, 7 of the condenser 5 and the radiator 9 are provided at a constant pitch so that the respective fins 4, 8 can be inserted, as shown in FIG. The pitch is set the same for both heat exchangers. Further, the tube 3 of the condenser 5 and the tube 7 of the radiator 9 are arranged apart from each other by a predetermined distance in the ventilation direction (the horizontal direction in FIG. 3).

The fins 4 of the condenser 5 and the fins 8 of the radiator 9 are formed by separate members, and the width of the fins of each heat exchanger is formed to be approximately half the width of the side plate 20 and the tubes 3 and 7 are formed. The fins 4 and 8 are attached so that both side edges of the fins 4 and 8 protrude from the side edges of the tubes 3 and 7. May be the same. The fins 4 of the condenser 5 and the fins 8 of the radiator 9 adjacent to the condenser 5 are brazed to the respective tubes in a state where they abut each other.

This state is also shown in FIGS. 4 (a) and 5, wherein the fins 4 of the condenser 5 and the fins 8 of the radiator 9 are bent between the tops 4a, 8a and between the tops. The fins 4 and 8 have peaks (or valleys) of the same pitch, are formed to have the same height and width, and the louvers 3 are provided on the flat portions 4b and 8b.
0 is formed. And the fin 4 of the capacitor 5
The fins 8 of the radiator 9 are attached, for example, with their phases shifted from each other, and are in point contact with the flat portions 4b, 8b in the middle of the side edges.

Each of the fins 4 and 8 is made of a bare material in which a brazing material is not clad, whereas the tube 3 of the condenser 5 and the tube 7 of the radiator 9 have a brazing material on the outer surface. 31 is made of a clad material clad. The fin 3b inserted into the tube 3 of the capacitor 5 is also made of a clad material in which the brazing material 31 is clad on both sides. Therefore, the brazing material 3 clad in each of the tubes 3 and 7
1, the tube and the fins arranged therebetween are brazed and the brazing material 31 clad on the fin 3b
As a result, the electric resistance welded tube 3a and the fin 3b are brazed to each other, and the adjacent fins 4, 8 are in a state of being simply in contact with each other.

Since the fins 4 of the condenser 5 and the fins 8 of the radiator 9 have the same shape, they can be molded simultaneously on the same production line. For example, as an example, the production shown in FIG. A way is being considered.

The method of manufacturing the fin will be described below. First, the fin material 50 for forming the fin is formed.
Is drawn out of the uncoiler 51 and is passed through the oil by the oil application device 32 to apply oil to the entire surface (oil application step). Thereafter, the fin material 50 is finely bent up and down by the louver forming machine 33 to form a corrugated shape, and at the same time, a louver is formed in a flat portion (louver forming step). Next, the fin pitch is temporarily packed between this device and the louver forming machine 33 by the pitch stuffing device 34 (pitch stuffing step), and then the intermediate stuffing device 35 and the pitch are set so that the fin pitch becomes the set pitch. It is adjusted by the feeding device 36 (pitch adjustment step). Then, counter 3
9 (for example, a worm that meshes with the fin material and sends out the fin material), counts the number of ridges of the fin material 50, and cuts the fin material that is continuous at every predetermined number of hills by the cutting machine 37. 40 (cutting step).

The fins 40 thus formed proceed to a sorting step, and are assigned to the sorting device 38 in FIG.
As shown in (c), the fins are turned sideways alternately left and right with respect to the moving direction of the fins. As a result, when viewed from above, one of the fins is shifted from the other fin by a phase of 180 ° C. (６ pitch) (see FIG. 6 (c)), and then the automatic operation of the heat exchanger is performed. In the assembling step, one of the thus formed fins having different phases is selectively picked up and assembled as the fin 4 of the capacitor and the other as the fin 8 of the radiator 9.

In the assembling step, the condenser 5 inserts the tubes 3 into the pair of headers 2a and 2b, assembles the fins 4 between the tubes, and the radiator 9
The first header member 16 and the second header member 17 are assembled by fitting the edge of the first header member 16 into the locking groove 22, and at the same time, the closing plate 18 is attached to the header members 16, 17.
And the first header member 16
And insert the fins 8 between the tubes 7.
Assemble. Further, a side plate 20 is attached to the outside of the stacked tubes 3 and 7 via fins 4 and 8.

Here, the fins may be assembled in separate steps for each heat exchanger, but the components of the condenser 5 and the radiator 9 excluding the fins 4 and 8 are assembled first. After arranging the heat exchangers 5 and 9 side by side so that the heat exchange sections of the heat exchangers 5 and 9 face each other in parallel,
Fins 4 and 8 may be assembled at the same time.

The assembled heat exchangers 5 and 9 are arranged such that their heat exchange portions face each other in parallel, and the headers 2 a and 2 b of the condenser 5 and the headers 6 a and 6 a of the radiator 9.
6b is disposed adjacent to the tubes 3 and 7 in such a manner that the joint portions thereof are arranged side by side, and the phases of the adjacent fins 4 and 8 between the adjacent heat exchangers are shifted by 1/2 pitch. In contact with each other and fixed by a jig to maintain this state. Thereafter, if the whole is brazed in a furnace, the condenser 5 and the radiator 9 are integrally connected via the side plate 20.

In the process of assembling the fins 4 and 8 or after each assembly, the capacitor 5 and the radiator 9 may be placed so as to be vertically overlapped. In this case,
Even when the fins 4 and 8 of both heat exchangers are separated, the upper fin is displaced by its own weight and contacts the lower fin. Therefore, even if the adjacent fins 4 and 8 are not intentionally brought into contact with each other, the adjacent fins come into contact with each other after the in-furnace brazing is completed.

Such a parallel-integrated heat exchanger 1 is mounted in an engine room of a vehicle with the condenser 5 upstream, and a high-temperature and high-pressure refrigerant flows into the condenser 5 from a compressor (not shown). In the process of passing through the tube 3, heat is transmitted to the fins 4 and exchanges heat with the air passing between the fins. Further, in the radiator 9, engine cooling water flows in. Similarly, in the engine cooling water, heat is transmitted to the fins 8 in the process of passing through the tube 7 and exchanges heat with the air passing between the fins 8.

In a conventional configuration in which the fins are formed integrally with both heat exchangers, or in a configuration in which the joining area is increased even when the fins are separate, the temperature of the radiator becomes higher than the temperature of the condenser. It is feared that the heat of the capacitor is transmitted to the capacitor via the fins, and the heat exchange performance of the capacitor is reduced. However, according to the above configuration, the fins 4 and 8 are separately formed by the capacitor 5 and the radiator 9, In addition, since the adjacent fins are merely in contact with each other with the phase shifted, the contact state between the fins 4 and 8 may be changed due to the variation in the manufacturing process or the shape of the contact end face. Therefore, heat transfer by the fins from the radiator 9 to the capacitor 5 can be reduced as compared with the related art. Thereby, the heat exchange performance of the condenser 5 can be made less likely to be affected by the heat from the radiator 9.

In the above-described configuration, as the best mode, the adjacent fins of the capacitor 5 and the radiator 9 are brought into contact with the phases shifted from each other, but the fins are joined by a brazing material or the like. Otherwise, the phases may be the same. Certainly, if the phase is the same, the contact area between the fins increases, so the amount of heat transfer also increases. However, as described above, the fins are simply in contact with each other, and the same Since it is not as surely adhered as the configuration, a certain reduction in heat transfer can be expected.

Further, in the above-described configuration, particularly, the advantage that the fins 4 of the condenser 5 and the fins 8 of the radiator 9 can be simultaneously manufactured in one manufacturing line, the existing equipment can be used, and the manufacturing process can be simplified. For example, a phase shift of 1/2 pitch between adjacent fins is considered for advantages such as the above. However, the present invention is not limited to this, and as shown in FIG. May be slightly shifted in phase, and the phase may be changed as appropriate.

Also, in the above-described configuration in which the phases are shifted, there may be cases where the phases of the fins are substantially the same due to variations in the manufacturing process. Needless to say,

Further, as shown in FIG. 7B, the contact area of the adjacent fins 4 and 8 may be reduced by using fins having different pitches in each heat exchanger. In this case, there are some places where the contact portion becomes large, but since there are generally many point contact points, it is possible to effectively suppress the transfer of heat from one fin to the other fin. The same effect can be obtained as in the above-described configuration in which the phases are shifted at the same pitch.

As long as the adjacent fins 4 and 8 are made of bare material, the tube 3 of the condenser 5 may be the above-described inner fin tube instead of the inner fin tube.
It may be constituted by a roll-formed tube shown in (b). This roll-formed tube is formed by folding a brazing sheet clad with a brazing material in two around the longitudinal direction, and forming a bead 3c protruding inward on an opposing flat surface.
The inside of the tube is divided into a number of flow paths by the beads 3c, and is itself formed by roll forming as disclosed in JP-A-9-323134 and JP-A-9-32997. It is formed by the method described above.

Further, in the above configuration, the fins 4 of the condenser 5 and the fins 8 of the radiator 9 have different fin plate thicknesses and louver shapes for each heat exchanger in accordance with the required performance of each heat exchanger. Alternatively, the materials of the fins may be different between the two heat exchangers.

In the above-described heat exchanger, an example in which the side plate 20 is formed as an integral member on the condenser side and the radiator side has been shown. However, as shown in FIG. The condenser 5 and the radiator 6 may be provided integrally on the outermost side of the heat exchange unit for each exchanger, and the side plates 41 and 42 of the two heat exchangers are joined to each other and brazed.

The temperature of the radiator 9 is controlled by the condenser 5
Is higher than the temperature of the side plate 20,
In the above case where both heat exchangers are integrally connected with each other by 41, 42, the side plates 20, 4
2 is joined to both headers 2a and 2b, and due to a difference in thermal expansion between the capacitor 5 and the radiator 9, the joint between the side plates 20, 42 and the headers 2a and 2b is fatigue-destructed due to long-term use. The headers 2a and 2b have holes, which may cause refrigerant leakage.

For this reason, as shown in FIG. 1B and FIG. 8A, on the capacitor side, if the side plates 20, 42 and the headers 2a, 2b are separated without being joined. Good. In the figure, the side plate 2
Although both ends of 0 and 42 are separated from both headers 2a and 2b, only one end is separated from the header to secure the strength, and the other end is brazed to the header. It may be. Further, in addition to such a configuration on the capacitor side, the side plates 20, 41 may be separated from at least one of the headers 6a, 6b also on the radiator side.

When the end portions of the side plates 20 and 41 and the header 6a or 6b of the radiator 9 are to be joined, even if the closing plate 18 is formed integrally with the side plate 20 or 41 in advance. Good. In the case of such a configuration, a cutout or a slit is provided in the first header member 16 so that the closing plate 18 following the side plate can be mounted on the header 6 in the same direction as the tube. The second header member 17 is replaced with the first header member 16.
The second header member 17 is extended longer than the second header member 17, and the closing plate 18 following the side plate is engaged with the protruding portion of the second header member 17, and at this time, the opening end of the header is closed by the closing plate 18. Is also good. Further, the connecting portion between the integrally formed side plate and the closing plate is bulged outward to form an arch shape, and the first header member 16 is inserted into the arched portion to form the side plate 20, 41 and the following closing plate 18 may be attached.

Even with the header structure of the radiator 9, the closing plate 18 is formed integrally with the first header member 16 for the purpose of reducing the number of components of the header 6 and simplifying the assembling work. Also, in the configuration in which the locking groove 22 of the second header member 17 is formed over the entire periphery so as to fit with the header member 16 of the first embodiment, the first header member may be provided with an insertion wall portion into which the tube 7 is inserted, On the side close to the capacitor 5, a side wall portion 16b formed following the insertion wall portion is formed in an L-shaped cross section, and the second header member is mounted on the first header member. The header 6 may be formed in a character shape or an arc shape in cross section, and the peripheral wall of the header 6 may be constituted by these header members.

Further, the second header member 17 is made of a resin, the first header member 16 is made of an aluminum alloy, and the integral brazing in a furnace is performed using another structure except for the second header member 17. The second header member 17 may be airtightly assembled to the first header member 16 after the members are assembled and after the brazing.

The condenser 5 and the radiator 9 have the same area of the heat exchanging section for exchanging heat with the passing air. As shown in FIGS. The exchange unit and the heat exchange unit of the radiator 9 may be different.

For example, in the side-by-side integrated heat exchanger 1 shown in FIGS. 9 and 10, the length of the condenser 5 in the stacking direction is shorter than the length of the radiator 9 in the stacking direction, and provided at the upper end of the condenser 5. The joining margin 43 bent from the side edge of the side plate 42 is extended upward along the end face of the radiator 9, and the joining margin 43 is brazed to the joining margin 44 bent from the side edge of the side plate 41 of the radiator 9. Configuration. In the drawing, the lower end of the capacitor 5 and the lower end of the radiator 9 are aligned. However, even if the upper ends are aligned and the side plates at the lower end are similarly joined by changing the length of the joint allowance, Capacitor 5
The upper and lower ends may be shifted so that is located at the center of the radiator 9. In each of the heat exchangers 5 and 9, the area of the heat exchange section is determined so as to obtain a predetermined heat exchange capacity. If necessary, the heat exchange section of the radiator 9 is connected to the heat exchange section of the condenser 5. The front area may be smaller than the replacement part.

The example of the side-by-side integrated heat exchanger shown in FIG. 11 shows a case where the lengths of the tubes 3 and 7 extending at right angles to the stacking direction in the condenser 5 and the radiator 9 are different. ing. In this example, the length A of the tube 3 of the condenser 5 is shorter than the length B of the tube 7 of the radiator 9 (A <B), and the respective heat exchangers 5 and 9 are the same as in FIG. And each side plate 4
1, 42, which are connected by brazing these side plates 41, 42. Even in such a configuration, depending on the case, the front area of the heat exchange section of the radiator 9 may be smaller than the front area of the heat exchange section of the condenser 5, or the condenser 5 and the radiator 9 may be integrally configured as a side plate. You may.

Further, as shown in FIG. 12, the dimension of the heat exchange portion of the condenser 5 is shortened in the laminating direction and the tube extending direction, and as shown in FIG. 43 may be joined to a joint margin 44 of the side plate 41 of the radiator 9.

Since the joint margin 43 of the capacitor 5 shown in FIG. 9 and FIG. 12 partially covers the heat exchange portion of the radiator 9, the space is set so as not to affect the heat exchange performance of the radiator 9. To form a plurality,
It is good to form a through-hole. In any configuration, a stopper for positioning may be provided at one of the joining margins 43 and 44. Further, in the above configuration, the capacitor 5 and the radiator 9 are joined (brazed) only by the side plate, but they are opposed to each other instead of or in addition to the side plate. Headers 2a, 2 of capacitors 5
b and the headers 6a and 6b of the radiator 9 may be joined (brazed). Also, joining the header of one heat exchanger and the side plate of the other heat exchanger may be considered.

In any of the above-described cases where the front area of the heat exchange section between the condenser 5 and the radiator 9 is different, the adjacent fins 4 and 8 between the opposing heat exchange sections are simply brought into contact without being brazed. This is the same, so that the heat transfer is reduced from one side of the heat exchanger to the other.

[0060]

As described above, according to the present invention,
In a side-by-side integrated heat exchanger that integrally connects a plurality of heat exchangers, the fins of each heat exchanger are formed with separate members, and the tubes are formed of a clad material in which a brazing material is clad. Since it is composed of bare material that is not clad with brazing material, even when adjacent fins come into contact with each other, they only come into contact with each other, reducing the amount of heat transmitted through the adjacent fins, A decrease in heat exchange performance can be suppressed.

Further, since the fins are formed as separate members for each heat exchanger, there is no need to worry about the strength of the fins as compared with the conventional fins having a common fin. Since the contact of the fin with the exchanger does not matter, the fin can be assembled without using the spacer, so that the production management can be facilitated and the number of production steps can be reduced.

Further, according to the present invention, the fins can be separated in each heat exchanger and assembled regardless of the phase of the fins. The specifications of the fins can be individually designed for each heat exchanger in accordance with the requirements, and the degree of freedom in design can be increased.

Further, if the adjacent fins are brought into contact with the phases shifted from each other between the opposing heat exchange sections, the fins can be in point contact, and the heat from one heat exchanger can be transferred to the other heat exchange section. Heat transfer to the exchanger can be further suppressed,
A decrease in the heat exchange performance of each heat exchanger can be further prevented.

Even when the fins of each heat exchanger are formed at different pitches instead of shifting the phases of the fins, most of the contact portions between the adjacent fins can be made point contacts, Similarly, heat transfer from one heat exchanger to the other heat exchanger is less likely to occur via the fins, and the heat exchange performance of each heat exchanger can be prevented from lowering.

In addition, since the fins are formed as separate members for each heat exchanger, the number of parts is increased as long as the fins are provided. However, the number of manufacturing steps and the number of mounting steps by integrating a plurality of heat exchangers are reduced. The simplification does not hinder the merits of the conventional integrated heat exchanger in that the heat exchanger can be reduced as compared with the case where each heat exchanger is manufactured separately. Rather, because each heat exchanger has separate fins,
The specifications of the fins can be set individually for each heat exchanger according to the manufacturing requirements and performance requirements of each heat exchanger.
There is no loss of design flexibility.

Further, if the fins of the first heat exchanger and the fins of the second heat exchanger are formed in the same shape and the phases of adjacent fins are shifted by ピ ッ チ pitch, the same fins can be formed. It can be used upside down, and the fins of each heat exchanger can be molded simultaneously with the same manufacturing equipment,
The number of manufacturing steps and costs can be reduced.

The adjacent heat exchangers may have different sizes of the front area of the heat exchange portion as long as the fins are in contact with each other. Each heat exchange part with the vessel has a different length in the stacking direction, even if the length in the direction of extension of the tube orthogonal to the direction of stacking is different. The length may be different.

Even when such heat exchangers having heat exchange portions having different areas are connected to each other, since the fins are not simply brought into contact with each other and are not brazed, the heat exchangers from one heat exchanger to the other heat exchanger are not used. Heat transfer to the fins is less likely to occur,
A decrease in the heat exchange performance of each heat exchanger can be prevented.

[Brief description of the drawings]

FIG. 1 shows the overall configuration of a parallel-integrated heat exchanger according to the present invention. FIG. 1 (a) is a front view in which a middle part is omitted, and FIG. FIG. 2 is a plan view of FIG.

FIG. 2 is a perspective view showing a header of the side-by-side integrated heat exchanger according to FIG. 1 and the vicinity thereof;

FIG. 3 is a sectional view taken along line AA of FIG. 2;

FIG. 4 is a diagram showing a state in which the fins of the condenser and the fins of the radiator are brought into contact with their phases shifted from each other. FIG. 4 (a) shows a configuration using an inner fin tube as the condenser tube. FIG. 4B shows a configuration using a roll-formed tube as the tube of the capacitor.

FIG. 5 shows fins and tubes of a condenser;
FIG. 4 is an enlarged view showing fins and tubes of the radiator.

FIG. 6 is a diagram showing a manufacturing process of a fin used in the present heat exchanger.

FIG. 7A shows a state in which the fins of the condenser and the fins of the radiator are joined together with a small phase shift, and FIG. 7B shows a case where the pitch of the fins of the heat exchangers is different. This shows the state in which

8 is a view showing another connection structure of the side-by-side integrated heat exchanger according to the present invention. FIG. 8 (a) is a plan view thereof, and FIG. 8 (b) is a perspective view thereof. FIG.

FIG. 9 is a front view showing an example in which the length of one of the heat exchangers in the stacking direction is shortened in the side-by-side integrated heat exchanger according to the present invention.

FIG. 10 is a view showing a connection state of stacked end portions of the side-by-side integrated heat exchanger of FIG. 9; FIG.
Is a perspective view thereof, and FIG. 10B is a side sectional view thereof.

FIG. 11 is a view showing an example in which the length of the tube of one of the heat exchangers in the extension direction is shortened in the side-by-side integrated heat exchanger according to the present invention, and FIG. FIG. 11B is a plan view thereof.

FIG. 12 is a front view showing an example in which the length in the stacking direction of one of the heat exchangers and the length in the direction in which the tubes extend in the side-by-side integrated heat exchanger according to the present invention.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Parallel integrated heat exchanger 2a, 2b, 6a, 6b Header 3, 7 Tube 4, 8 Fin 5 Condenser 9 Radiator 31 Brazing material

Claims (10)

[Claims] 1. A plurality of heat exchangers each having a heat exchange section formed by alternately stacking fins and tubes are arranged in front of and behind the airflow direction. The fins of the heat exchangers are integrally formed so as to face each other, the fins of the heat exchangers are formed of separate members, the tube is formed of a clad material clad with a brazing material, and each of the fins is formed of a brazing material. A side-by-side integrated heat exchanger characterized by comprising a bare material not clad. 2. A header comprising a corrugated fin and a plurality of tubes laminated via the fin, constituting a heat exchange section, and extending in the direction in which the plurality of tubes are laminated and communicating with each tube. Wherein the first and second heat exchangers are coupled such that the respective heat exchange portions face each other in the same stacking direction of the tubes. The fin of the first heat exchanger and the fin of the second heat exchanger are formed by separate members, and the tube is clad with a brazing material. Wherein each of the fins is made of a bare material on which a brazing material is not clad. 3. The side-by-side integrated heat exchanger according to claim 1, wherein the fins of the heat exchangers adjacent to each other between the opposing heat exchange sections are shifted in phase. 4. The fin of the first heat exchanger and the fin of the second heat exchanger.
4. The side-by-side integrated heat exchanger according to claim 3, wherein the heat exchanger fins are formed in the same shape as the fins, and the phases are shifted by ピ ッ チ pitch. 5. The heat exchanger according to claim 3, wherein the fins of the heat exchangers adjacent to each other between the opposing heat exchange units are formed at different pitches, instead of shifting the phases of the fins. Side-by-side integrated heat exchanger. 6. The tube according to claim 1, wherein the tube forming the at least one heat exchanger is an inner fin tube formed by inserting a fin into an electric resistance welded tube. A side-by-side integrated heat exchanger as described. 7. The tube forming at least one of the connected heat exchangers is a tube formed by roll forming with a brazing sheet.
A side-by-side integrated heat exchanger according to any one of the above. 8. The side-by-side integrated type according to any one of claims 2 to 7, wherein the first heat exchanger and the second heat exchanger have different lengths in the stacking direction. Heat exchanger. 9. The heat exchanger according to claim 2, wherein the first heat exchanger and the second heat exchanger have different lengths in an extending direction of the tube orthogonal to the stacking direction. 4. The side-by-side integrated heat exchanger according to any one of the above. 10. The first heat exchanger and the second heat exchanger are different in a length in the stacking direction and a length in an extension direction of the tube orthogonal to the stacking direction. 8. The side-by-side integrated heat exchanger according to any one of 2 to 7.