JP2004301455A - Header tank for heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a header tank for a heat exchanger, maintaining pressure resistance and reducing its size while securing the passage cross section area of a pipe. <P>SOLUTION: The pipe 32 of the header tank 3 is formed by combining two split bodies 32A, 32B. The first split body 32A in an approximate U-shape has a tube retaining wall portion 34 into which a flat tube 30 is inserted and a pair of straight portions 36, 36 protruded from the tube retaining wall portion 34 via angle R-portions 35, 35 to an approximately perpendicular direction. Thus, a depth for the tube 30 to be inserted is set smaller than in a sectionally circular header tank, and a smaller size is achieved while securing the passage cross section area. Still, because a cylindrical protruded portion 37 protruded from the tube retaining wall portion 34 inward to the pipe 32 for retaining the tube 30 extends over both angle R-portions 35, 35, the angle R-portions 35, 35 and their vicinity where stress is concentrated during receiving refrigerant pressure are reinforced. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a header tank for a heat exchanger such as a condenser used for an air conditioner such as an automobile.
[0002]
[Prior art]
2. Description of the Related Art As a heat exchanger of an air conditioner, there is a heat exchanger as disclosed in Patent Document 1. FIGS. 5 and 6 show a heat exchanger (a condenser in this example) described in Patent Document 1. FIG. As shown in FIG. 5, the condenser 1 as a heat exchanger is configured by connecting the openings at both ends of flat tubes 13 arranged in multiple stages to a pair of opposed header tanks 11 and 12. . Corrugated fins 14 are interposed between the flat tubes 13 arranged in multiple stages.
[0003]
Each of the header tanks 11 and 12 includes a pipe 15, a closing member 16 for closing both ends of the pipe 15, and a partition plate 17 for partitioning a passage extending in the pipe 15 in the longitudinal direction. In this example, the closing member also serves as a joint with the outlet pipe or the inlet pipe.
[0004]
As shown in FIGS. 5 and 6, a number of tube insertion holes 18 for inserting the tubes 13 are formed in the pipes 15 constituting the header tanks 11 and 12 by press working. After the tube 13 is inserted into the tube, the fin 14 and the periphery of the tube 13 and the insertion hole 18 are fixed by brazing so that the refrigerant does not leak from the insertion hole 18.
[0005]
In the condenser 1 configured as described above, the flowing refrigerant flows in the tube 13 so as to meander between the one header tank 11 and the other header tank 12 by the partition 17. The refrigerant flowing in the tube 13 radiates heat to the air passing through the gap between the fins 14 interposed between the tubes 13, 13, and at this time, the refrigerant itself is cooled. Therefore, the refrigerant introduced into the condenser in a gaseous state is drawn out of the condenser in a liquid state.
[0006]
[Patent Document 1]
JP-A-7-27496
[Problems to be solved by the invention]
FIG. 7 is an exploded perspective view of a conventional pipe, and FIG. 8 is a cross-sectional view of the conventional pipe. As shown in FIGS. 7 and 8, the conventional pipe 15 is configured by combining two semi-cylindrical divided bodies 19 and 20 in order to secure pressure resistance as a header tank for a heat exchanger for flowing a refrigerant. Its cross-sectional shape is formed in a circular cross section. A substantially L-shaped receiving portion 19a for positioning the opening peripheral portion 20a of the other divided body 20 is formed on one of the divided bodies 19 constituting the pipe 15.
[0008]
However, in the conventional header tanks 11 and 12 for the heat exchanger, since the pipe 32 has a circular cross-section, the insertion depth of the tube 13 is deep as shown in FIG. 9B, and the passage cross-sectional area of the pipe 15 is secured accordingly. Therefore, the diameter of the pipe 15 needs to be increased, and the header tanks 11 and 12 tend to be large.
[0009]
Against this background, the present inventor has conceived a structure in which the depth of insertion of the tube can be reduced and the size of the pipe can be reduced by forming the first divided body into a substantially U-shape as shown in FIG. 9A. In addition, a header tank having such a structure and excellent pressure resistance has been realized.
[0010]
That is, an object of the present invention is to provide a header tank for a heat exchanger that can maintain a pressure resistance and can be downsized while securing a passage cross-sectional area of a pipe.
[0011]
[Means for Solving the Problems]
The invention according to claim 1 is a header tank of a heat exchanger in which a plurality of flat tubes arranged in multiple stages are connected to at least a pair of header tanks.
The header tank is configured to include a pipe formed by combining two divided bodies divided along a longitudinal direction, and a closing member that closes both ends of the pipe,
The first divided body includes a tube holding wall portion having an insertion hole into which a flat tube is inserted, and a pair of straight portions projecting from the tube holding wall portion in a substantially orthogonal direction via a corner R portion. U-shaped,
The peripheral portion of the tube insertion hole is configured as a cylindrical protruding portion that protrudes inward of the pipe and holds the tube,
The cylindrical projection is extended over both corners R.
[0012]
According to a second aspect of the present invention, in the header tank for a heat exchanger according to the first aspect, the corner R portion is provided with a concave portion recessed inwardly of the pipe in a zigzag manner with a tube insertion hole. It is characterized by the following.
[0013]
【The invention's effect】
According to the first aspect of the present invention, the insertion depth of the tube can be set shallower than that of the header tank having a substantially circular cross section by setting the first divided body in a substantially U-shape, and the equivalent passage cross-sectional area is obtained. While minimizing the size in the longitudinal direction of the tube. Moreover, since the cylindrical protruding portion extends over both corners R, the corner R where stress is concentrated when receiving refrigerant pressure and the vicinity thereof can be reinforced.
[0014]
Thus, it is possible to provide a header tank for a heat exchanger that can maintain its pressure resistance and can be downsized while securing a cross-sectional area of the pipe passage.
[0015]
According to the second aspect of the present invention, in addition to the effects of the first aspect of the invention, a tube insertion hole (cylindrical projecting portion) and a stair-like concave recessed inward of the pipe are provided at the corner R portion. Since it is provided, the corner R portion and the vicinity thereof can be further reinforced, and a structure having more excellent pressure resistance can be obtained.
[0016]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, an embodiment of the present invention will be described with reference to the drawings. Note that the overall structure of the heat exchanger is the same as that of the conventional heat exchanger, and a description thereof will be omitted.
[0017]
FIG. 1 is a perspective view of a pipe of a header tank according to the present invention, and FIG. 2 is a sectional view taken along the line II-II in FIG. 3 is a view taken in the direction of arrows III-III in FIG. 1. FIG. 3 is a view showing a disassembled state of the pipe, and FIG. 3b is a view showing a state of inserting the tube into the tube.
[0018]
The header tank 31 of this embodiment includes a pipe 32, a closing member (not shown) that closes both ends of the pipe 32, and a partition plate (not shown) that divides a longitudinally extending passage in the pipe 32. Have been.
[0019]
Hereinafter, the pipe 32 will be described in detail.
[0020]
As shown in FIGS. 1 to 3, the pipe 32 is formed in a tubular shape by combining two divided bodies 32 </ b> A and 32 </ b> B divided along the longitudinal direction.
[0021]
The first divided body 32A includes a tube holding wall portion 34 and a pair of straight portions 36 projecting from both ends of the tube holding wall portion 34 in a direction substantially orthogonal to each other, and is formed in a substantially U-shape. I have.
[0022]
The tube holding wall portion 34 is formed in a flat plate shape orthogonal to the longitudinal direction of the tube 30, and has insertion holes 34a, 34a,... For inserting and holding the flat tube 30. The peripheral portion of the tube insertion hole 34 a is formed as a cylindrical projecting portion 37 projecting inward from the pipe 32 and holding the tube 30. Further, the pair of straight portions 36 project from the tube holding wall portion 34 in a substantially orthogonal direction via the corner R portions 35, and both ends 30a, 30a in the width direction of the tube 30 (two-dot chain line in FIG. 1). Are provided along the extension direction. The base end of the straight portion 36 is set close to both ends 30 a, 30 a in the width direction of the tube 30.
[0023]
On the other hand, the second divided body 32B includes a main body 41 that closes the U-shaped opening of the first divided body 32A. Both ends of the main body 41 are configured as abutting portions 42 against which the distal end surface 36a of the straight portion 36 of the first divided body 32A abuts. In addition, a joining projection 43 that is joined to the inner peripheral surface 36b at the distal end of the straight portion 36 protrudes from the inner peripheral surface 41a of the main body 41. That is, the L-shaped joint surfaces 42a and 43a that are open on the outer side of the second divided body 32B that are in contact with the distal end of the straight portion 36 of the U-shaped first divided body 32A are formed.
[0024]
The main body portion 41 of the second divided body 32B is formed so as to connect the butting portions 42, 42 in a substantially straight line and to be substantially orthogonal to the longitudinal direction of the tube 30. As a result, the pipe 32 composed of the first divided body 32A and the second divided body 32B has a quadrangular cylindrical cross section.
[0025]
The inner peripheral surface 41a of the main body portion 41 of the second divided body 32B has a circular curved shape in which a pair of joining projections 43, 43 are connected with a smooth surface, and the circular curved surface 41a is a curved surface that bulges outward. is there.
[0026]
The pipe 32 configured as described above is composed of a first divided body 32A and a two-divided body 32B sandwiched between predetermined portions of a partition plate (not shown), and then the straight portions 36, 36 are connected to the second divided body 32B. Are temporarily fixed by caulking toward the joining projections 43, 43, and are brazed in this state to manufacture. More specifically, the heat exchanger is manufactured by integrally brazing and fixing the temporarily fixed pipe 32 to a joint block, a closing member, a tube, a fin, a side plate, and the like.
[0027]
Here, the thickness d2 along the crimping direction of the base end portions of the joining projections 43, 43 of the second divided body 32B is larger than the thickness d1 of the straight portion 36 of the first divided body 32A as shown in FIG. It is formed thick. For this reason, it is possible to prevent the joining protrusion 43 from being deformed even when receiving the caulking force.
[0028]
This embodiment has the following two features in particular.
[0029]
First, the cylindrical projecting portion 37 extends across both corners R portions 35, 35.
[0030]
Secondly, the corner R portion 35 has a tube insertion hole 34a and a concave portion 38 that is concavely inwardly formed in a pipe in a staggered manner.
[0031]
According to the header tank 31 for a heat exchanger of such an embodiment, the following effects are obtained.
[0032]
First, the insertion depth of the tube 30 can be set shallower than the conventional header tanks 11 and 12 having a circular cross section by setting the first divided body 32A to have a substantially U-shape. Thereby, while ensuring the same passage cross-sectional area as the conventional header tanks 11 and 12 having a circular cross section, it is possible to reduce the size in the longitudinal direction of the tube 30 more than the conventional header tanks 11 and 12 having a circular cross section (FIG. 9). In addition, since the cylindrical projecting portion 37 extends over both corners R, 35, the corner R where the stress is concentrated when receiving the refrigerant pressure and the vicinity thereof can be reinforced. Thus, the header tank 31 for the heat exchanger can be downsized while maintaining the pressure resistance and securing the passage cross-sectional area.
[0033]
Secondly, since the tube insertion hole 34a (the cylindrical projecting portion 37) and the concave portion 38 recessed inwardly of the pipe are provided in the corner R portion 35, the corner R portion 35 and its vicinity are further strengthened. The structure can be reinforced and more excellent in pressure resistance.
[0034]
Third, since the tube holding wall portion 34 of the first divided body 32A has a flat plate shape orthogonal to the longitudinal direction X of the tube 30, the size can be further reduced in the longitudinal direction X of the tube. In the present invention, as shown in FIG. 4, a curved tube holding wall portion 71 may be used as long as the curvature is larger than the corner R portion 35.
[0035]
Fourth, the second divided body 32B of the header tank 31 is provided at both ends of the main body 41 with the abutting portion 42 against which the distal end surface 36a of the straight portion 36 of the first divided body 32A abuts, And a joint projection 43 that is provided to project from the inner peripheral surface 41a of the straight portion 36 and is joined to the inner peripheral surface 36b of the tip of the straight portion 36. The first divided body 32A and the second divided body 32B can be combined without protruding from the straight portion 36 of the divided body 32A in the width direction Y of the tube 30. For this reason, the header tank 31 (pipe 32) can be reduced in the width direction Y of the tube 30 as compared with the conventional structure in which the joining protrusions 21 are provided on the outside.
[0036]
In addition, the cross-sectional shape of the header tank 31 becomes closer to a circular shape due to the presence of the joining projections 43, 43, so that the durability of the header tank 31 is further improved. Note that the tip end surface 36a of the straight portion 36 does not necessarily have to be in contact with the butting portion 42. That is, when the size of the partition plate interposed in the pipe 32 is set to be large, the abutting portion 42 and the distal end surface 36a of the straight portion 36 may be separated from each other.
[0037]
Fifth, since the main body 41 of the second divided body 32B is formed in a straight line, the header tank 31 (the pipe 32) can be further downsized along the longitudinal direction X of the tube 30.
[0038]
Sixth, since the inner peripheral surface 41a of the main body portion 41 of the second divided body 32B is a circular curved surface, it is possible to reduce the size of the pipe 32 and to form the entire inner peripheral surface of the pipe with a polygonal cross section. Superior in pressure resistance compared to
[0039]
Sixth, since the first divided body 32A and the second divided body 32B are temporarily fixed to each other by caulking of the straight portion 36 of the second divided body 32B, the first divided body 32A and the second divided body 32 are brazed at the time of brazing. A jig for temporarily holding the 32B is unnecessary, and wasteful heat capacity is not wasted.
[0040]
Seventh, the base ends of the joining projections 43, 43 of the second divided body 32B are thicker than the straight portions 36 of the first divided body 32A along the caulking direction (in this example, the width direction Y of the tube). Since it is formed, the joining projections 43, 43 of the second divided body 32B do not fall down due to the caulking force, and the first divided body 32A and the second divided body 32B can be reliably temporarily fixed.
[0041]
As described above, according to the present invention, since the first divided body into which the flat tube is inserted has a U-shape, the insertion depth of the tube can be set shallower than that of a conventional header tank having a circular cross section. Thus, the header tank can be downsized in the longitudinal direction of the tube while ensuring the cross-sectional area of the passage. In addition, since the cylindrical protruding portion that protrudes inward from the tube holding wall and holds the tube extends across both corners R, the corner R where stress is concentrated when subjected to refrigerant pressure And its vicinity can be reinforced. As a result, the header tank for the heat exchanger can be downsized while maintaining the pressure resistance and securing the cross-sectional area of the passage.
[0042]
In the above-described embodiment, the structure is provided with the concave portion at the corner R portion. However, the present invention may of course be a structure without the concave portion.
[0043]
In addition, the present invention can be applied to various heat exchangers such as a radiator, a condenser, and an evaporator. In particular, the width of the header tank is larger than that of the heat exchange section (core section) including tubes and fins. 5 is particularly effective because the maximum outer diameter can be reduced while improving the pressure resistance.
[Brief description of the drawings]
FIG. 1 is a perspective view of a pipe of a header tank according to the present invention.
FIG. 2 is a sectional view taken along the line II-II in FIG.
3 is a view taken in the direction of arrows III-III in FIG. 1. FIG. 3 is a view showing a disassembled state of the pipe, and FIG. 3b is a view showing a state of inserting the tube into the tube.
FIG. 4 is a view showing a modified example of a pipe.
FIG. 5 is a perspective view showing a condenser as a conventional heat exchanger.
FIG. 6 is a vertical sectional view of a header tank of the condenser.
FIG. 7 is an exploded perspective view of a pipe of a header tank for the condenser.
FIG. 8A is an exploded cross-sectional view of a pipe of a header tank for the condenser, and FIG. 8B is a cross-sectional view showing a state of inserting the tube of the header tank.
FIG. 9 is a diagram showing a difference in the outer diameter of the tube from the conventional header tank in the longitudinal direction. FIG. 9A is a sectional view of the header tank according to the present invention, and FIG. Sectional drawing of a header tank.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Heat exchanger 30 ... Tube 31 ... Header tank 32 ... Pipe 32A ... 1st divided body 32B ... 2nd divided body 34 ... Tube holding wall part 34a ... Tube insertion hole 35 ... Corner R part 36 ... Straight part 37 ... Cylindrical projection 38 ... Recess 71 ... Tube holding wall

Claims (2)

A header tank (31) of a heat exchanger in which a plurality of flat tubes (30) arranged in multiple stages are communicatively connected to at least a pair of header tanks (31, 31),
The header tank (31) includes a pipe (32) formed by combining two divided bodies (32A, 32B) divided along a longitudinal direction, and a closing member that closes both ends of the pipe (32). , Comprising
The first divided body (32A) is projected from the tube holding wall portion (34) into which the flat tube (30) is inserted, and from the tube holding wall portion (34) in a substantially orthogonal direction via a corner R portion (35). And a pair of straight portions (36, 36) are provided.
The periphery of the tube insertion hole (34a) is formed as a cylindrical protrusion (37) projecting inward from the pipe (32) and holding the tube (30);
A header tank (31) for a heat exchanger, wherein the cylindrical projecting portion (37) extends over both corners (35, 35). The header tank (31) for a heat exchanger according to claim 1, wherein:
A header tank (31) for a heat exchanger, wherein the corner R portion (35) is provided with a tube insertion hole (34a) and a concave portion (38) recessed inwardly in a pipe in a staggered manner.

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