WO2002021056A1

WO2002021056A1 - Heat exchanger for stirling refrigerating machine, heat exchanger body, and method of manufacturing heat exchanger body

Info

Publication number: WO2002021056A1
Application number: PCT/JP2001/007515
Authority: WO
Inventors: Hitoshi Mochizuki; Yoshiaki Ogura
Original assignee: Sharp Kabushiki Kaisha
Priority date: 2000-09-01
Filing date: 2001-08-30
Publication date: 2002-03-14
Also published as: CN1483129A; EP1314938B1; BR0114038A; CA2419724A1; EP1314938A1; KR20030028830A; KR100523776B1; DE60110813T2; TW552384B; BR0114038B1; DE60110813D1; ES2240502T3; CA2419724C; CN1206489C; EP1314938A4

Abstract

A heat exchanger for Stirling refrigerating machine, comprising annular corrugated fins formed cylindrically by forming a sheet having a large number of grooves provided therein by corrugating forming so that the grooves are positioned parallel with the axial direction of the cylindrically formed fins and an inside ring-shaped member coming into contact with the inner peripheral surface of the annular corrugated fins formed integrally with each other, wherein the heat exchanger is inserted into the hollow of a tubular body to provide a radiator or a heat sink for Stirling refrigerating machine.

Description

Description Heat exchanger for Stirling refrigerator, heat exchanger body, and method for manufacturing heat exchanger body

The present invention relates to a heat exchanger body such as a heat absorber and a radiator provided in a Stirling refrigerator, a heat exchanger thereof, and a method of manufacturing the heat exchanger body. Background art

First, a general configuration of a free piston type Stirling refrigerator using a stirling engine will be described. FIG. 29 is a diagram schematically showing a side cross section of a free piston type Stirling refrigerator. In the cylinder 1, a heat absorber 2, which is a low temperature part, a regenerator 3, and a radiator 4, which is a high temperature part, are accommodated in this order. Each of the heat absorber 2 and the radiator 4 is a heat exchanger body in which the heat exchangers 22 and 42 are attached to the inner peripheral surface on one end side of the tubular main bodies 21 and 41, respectively. Reference numerals 2 and 42 are adjacent to the regenerator 3 in the cylinder 1.

In the cylinder 1, a displacer 6 fixed to one end of the display salod 5 and a biston 7 penetrated by the display salad 5 are provided. The other end of the display salod 5 is connected to a spring 8. In the cylinder 1, the displacer 6 and the bistone 7 form an expansion space 9 inside the heat absorber 2 and a compression space 10 inside the heat radiator 4. The expansion space 9 and the compression space 10 communicate with each other by the regenerator 3 to form a closed circuit.

The operation of this free-biston type stirling refrigerator will be described. The piston 7 reciprocates at a predetermined cycle in the axial direction of the cylinder 1 by external power such as a linear motor (not shown). A working gas such as helium is previously sealed in the compression space 10.

When the working gas in the compression space 10 is compressed by the movement of the biston 7, the working gas is guided to the expansion space 9 through the regenerator 3 via the heat exchanger 42 of the radiator 4 (see FIG. , Dotted arrow A). At this time, the working gas that generated heat by compression is The heat is exchanged with the external air in 2 to release the heat, and the heat passes through the regenerator 3 to receive the cold stored in the regenerator 3 in advance and is precooled.

When the working gas flows into the expansion space 9, the displacer 6 is pushed rightward against the spring 8, so that the working gas expands and generates cold heat. When the working gas expands to some extent, the displacer 6 is pushed back in the opposite direction by the return force of the spring 8.

As a result, the working gas in the expansion space 9 passes through the heat exchanger 22 of the ripening device 2, passes through the regenerator 3, and moves again to the compression space 10 (solid arrow A 'in the figure). At this time, the working gas is heat-exchanged with the external air in the heat exchanger 22 to absorb the heat, and passes through the regenerator 3 to receive the heat stored in the regenerator 3 and is preheated. You. Then, the working gas that has returned to the compression space 10 is again compressed by the biston 7.

By repeating such a series of cycles continuously, extremely low-temperature cold heat is extracted in the heat absorber 2. Here, it is preferable that the amount of heat absorbed by the heat exchanger 22 of the heat absorber 2 and the amount of heat released by the heat exchanger 42 of the radiator 4 be larger. This is because the efficiency of the pre-cooling and pre-heating of the regenerator 3 with respect to the working gas is improved, so that the load on the regenerator 3 can be reduced, and the refrigeration performance of the Stirling refrigerator can be improved.

Next, the radiator 4, which is the high-temperature side heat exchanger of the above-described Stirling refrigerator, will be described with reference to FIG. Here, only the radiator 4 and its heat exchanger 42 will be described, but the heat absorber 2 and its heat exchanger 22, which are the low-temperature side heat exchangers, have the same configuration.

As shown in FIG. 30, this heat exchanger 42 is an annular corrugated fin 42 1 formed by forming a corrugated thin plate into a cylindrical shape. A large number of V-shaped grooves 421a extending linearly along the axial direction are formed at regular intervals, and have a jagged shape.

Here, the portion of the radiator 4 protruding toward the center of the main body 41 is defined as the bottom 4 21 b of each groove 4 21 a, and the portions protruding toward the inner peripheral surface of the main body 41 are adjacent to each other. Let it be the top 4 2 1c formed by the groove 4 2 1a. The diameter of the circle (the outer diameter of the annular corrugated fin 4 21) formed by smoothly connecting the tops 4 2 1 c and the inner diameter of the main body 4 1 are almost the same. Equally, the main body 41 and the annular corrugated fin 42 1 are arranged such that their axes are concentric.

The inner peripheral surface of the main body 41 and the top 4 21 c of the annular corrugated fin 42 1 are firmly fixed with an adhesive or solder. FIG. 31 is an enlarged view of an essential part of the annular corrugated fin 4 21 as viewed from the axial direction, and shows a state where it is fixed with an adhesive. In this case, first, the adhesive 11 is spread thinly on the inner peripheral surface of the main body 41, and the annular corrugated fins 42 21 are inserted there. Then, the adhesive 11 is dried while the annular corrugated fin 4 21 is held at a predetermined position for a while.

FIG. 32 shows a state of being fixed with solder. In the case of soldering, first, the annular corrugated fin 421 is inserted into the main body 41. Then, while holding the annular corrugated fins 421 in a predetermined position, soldering is performed on a portion where the inner peripheral surface of the main body 41 and the top portion 421c of the annular corrugated fins 421 are in contact with or close to each other. Apply 1 2.

However, in the above-described conventional heat exchanger body, the fixing step by bonding or soldering is performed manually. Therefore, this process is very laborious and time-consuming, so that the productivity is low and it is difficult to reduce the manufacturing cost. In addition, the quality of the product, that is, the heat exchange performance tends to vary, and the product lacks stability and reliability.

Furthermore, if the annular corrugated fin 421 was damaged due to long-term use of the Stirling refrigerator, it could not be removed and replaced. Therefore, there were problems in terms of the economic burden on the user at the time of repair and the recycling of resources in consideration of the global environment, so-called recycling. Disclosure of the invention

The present invention has been made to solve the above problems. That is, a heat exchanger for a Stirling refrigerator of the present invention comprises: an annular corrugated fin obtained by forming a thin plate having a number of grooves formed by corrugation into a cylindrical shape so that the grooves are parallel to an axial direction; The annular corrugated fin is formed integrally with an inner ring-shaped member that is in contact with the inner periphery.

If these annular corrugated fins and the inner ring-shaped member are integrated, Their contact area increases, and they show good thermal conductivity. In addition, the integration facilitates handling of the heat exchanger and enables replacement and repair. Therefore, it is very economical and recyclable. In addition, it is preferable to apply bonding means, such as brazing or soldering, for the integration.

And the heat exchanger body of the present invention is obtained by inserting the above heat exchanger for a Stirling refrigerator into the hollow of the tubular main body. In this case, if the inner diameter of the main body is slightly smaller than the outer diameter of the heat exchanger, the heat exchanger can be attached to the main body by crimping without bonding or welding. Furthermore, if at least one end of the main body is formed with a taper such that the wall thickness becomes thinner toward the end along the axial direction, the penetration may be reduced.

Around the annular corrugated fin, corrugated projections are formed in close contact with each other and are arranged at equal intervals as a whole, and corresponding to these projections, a corrugated recess is formed on one surface of the main body in the axial direction. When the heat exchanger is extended, by fitting the convex and concave parts when inserting the heat exchanger into the main body, the position of the heat exchanger in the main body can be prevented from shifting in the circumferential direction. .

Alternatively, a straight corrugated fin in which both ends of the inverted V-shaped groove at both ends are longer than the oblique side of the V-shaped groove between them is rounded into a cylindrical shape, and the ends are brought into contact with each other. The protruding portions formed at the ends of the both ends and protruding in the radial direction from the outer periphery of the annular corrugated fin are fitted into grooves extending in the axial direction on the inner surface of the main body. This prevents the position of the heat exchanger in the inside from shifting in the circumferential direction.

As a method of manufacturing the heat exchanger body, for example, a tubular introduction member tapered such that one end has substantially the same inner diameter as the main body and the wall thickness becomes thinner toward the other end is obtained by using the one end. A method of detachably attaching the heat exchanger for the Stirling refrigerator to the main body in the axial direction from the other end of the introduction member can be considered. In the heat exchanger body manufactured by this method, when the annular corrugated fin passes through the introduction member, the shape of the surrounding changes, so that the contact area with the inner surface of the main body increases. Therefore, the heat transfer efficiency of the annular corrugated fin is improved, and a heat exchanger body having excellent heat exchange performance can be provided. Further, the heat exchanger for a Stirling refrigerator of the present invention comprises: a ring-shaped korgut fin in which a thin plate having a large number of grooves formed by corrugating is formed into a cylindrical shape so that the grooves are parallel to the axial direction; It is formed by integrating an outer ring-shaped member in contact with the outer periphery of the corrugated fin.

When these annular corrugated fins and the outer ring-shaped member are integrated, their contact area increases, and good thermal conductivity is exhibited. In addition, the integration facilitates handling of the heat exchanger and enables replacement and repair. Therefore, it is very economical and recyclable. In addition, it is preferable to apply bonding means, such as brazing or soldering, for the integration.

The annular corrugated fin is formed by rolling a straight corrugated fin in which V-shaped grooves are continuously connected into a cylindrical shape, and forming one end of the V-shaped groove at one end and an inverted V-shaped groove at the other end. Can be easily manufactured by engaging and connecting with the end sides of.

Alternatively, a straight corrugated fin in which a V-shaped groove continuously extends is rounded into a cylindrical shape, and the end of the V-shaped groove at one end and the end of the inverted V-shaped groove at the other end are joined. The surfaces may be connected by spot welding to each other.

Alternatively, a straight corrugated fin in which V-shaped grooves are continuously connected is rounded into a cylindrical shape, and the end of the V-shaped groove at one end and the end of the inverted V-shaped groove at the other end are connected to each other. The connection may be made by bonding the surfaces.

Alternatively, a straight corrugated fin having a continuous V-shaped groove is rolled into a cylindrical shape, and the end of the V-shaped groove at one end and the end of the inverted V-shaped groove at the other end are mutually joined. The surfaces may be joined by applying a soldering to the surface.

Alternatively, a straight corrugated fin in which a V-shaped groove continuously extends is rounded into a cylindrical shape, and the opposite sides of the inverted V-shaped groove at both ends are held so that the surfaces thereof are in contact with each other. At this time, the connecting portions may be connected by attaching a joining member having a U-shaped cross section to the tip of the contact portion.

Alternatively, a straight corrugated fin in which V-shaped grooves are continuously connected is rounded into a cylindrical shape, and one end of the inverted V-shaped groove is formed on one end of the straight corrugated fin from one side to the other side. And the slit formed on the other side of the linear corrugated fin from one side to the other side of the inverted V-shaped groove at the other end of the linear corrugated fin. May be connected.

BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is an external perspective view of a radiator according to a first embodiment of the present invention.

FIG. 2A is an external perspective view showing a heat exchanger of the radiator.

FIG. 2B is an exploded perspective view of the heat exchanger.

FIG. 3 is an enlarged plan view of a part of the heat exchanger viewed from an axial direction.

FIG. 4 is a schematic vertical sectional view of the main body of the radiator and the heat exchanger.

FIG. 5 is an enlarged plan view of a part of the radiator viewed from the axial direction.

FIG. 6A is a plan view showing a linear corrugated fin.

FIG. 6B is an enlarged plan view showing a state in which the linear korgut fins are rounded and both ends are brought close to each other.

FIG. 6C is an enlarged plan view showing a part of the completed annular corrugated fin. FIG. 7 is an enlarged plan view of a part of the radiator according to the second embodiment of the present invention as viewed from the axial direction.

FIG. 8A is a plan view showing a straight corrugated fin.

FIG. 8B is an enlarged plan view showing a state where the straight corrugated fin is rolled and both ends are brought close to each other.

FIG. 8C is an enlarged plan view showing a part of the completed annular corrugated fin. FIG. 9 is an enlarged plan view of a part of the radiator according to the third embodiment of the present invention as viewed from the axial direction.

FIG. 10A is a plan view showing a linear korgut fin. FIG. 10B is an enlarged plan view showing a state where the straight corrugated fins are rounded and both ends are brought close to each other. '

FIG. 10C is an enlarged plan view showing a part of the completed circular corge tofin. FIG. 11 is an enlarged plan view of a radiator according to a fourth embodiment of the present invention as viewed from the axial direction.

FIG. 12A is a plan view showing a straight corrugated fin.

FIG. 12B is an enlarged plan view showing a state in which the straight corrugated fins are rolled and both ends are brought close to each other.

FIG. 12C is an enlarged plan view showing a part of the completed annular corrugated fin. FIG. 13 is an enlarged plan view of a part of a radiator according to a fifth embodiment of the present invention as viewed from the axial direction.

FIG. 14A is a plan view showing a straight corrugated fin.

FIG. 14B is an enlarged plan view showing a state where the straight corrugated fins are rolled and both ends are brought close to each other.

FIG. 14C is an enlarged plan view showing a part of the completed annular corrugated fin. FIG. 15 is an enlarged plan view of a part of a radiator according to a sixth embodiment of the present invention as viewed from the axial direction.

FIG. 16A is a plan view showing a straight corrugated fin.

FIG. 16B is an enlarged plan view showing a state where the straight corrugated fins are rolled and both ends are brought close to each other.

FIG. 16C is an enlarged plan view showing a part of the completed annular corrugated fin. FIG. 17 is an enlarged perspective view showing a main part of FIG. 16B. FIG. 18 is an enlarged plan view of a radiator according to a seventh embodiment of the present invention as viewed from the axial direction.

FIG. 19A is a plan view showing a straight corrugated fin.

FIG. 19B is a plan view showing an annular corrugated fin formed by rolling a straight corrugated fin and contacting both ends.

FIG. 19C is a top view of the cylindrical main body. FIG. 20 is an external perspective view of a part of a radiator according to an eighth embodiment of the present invention. FIG. 21A is an external perspective view showing a heat exchanger of the radiator.

FIG. 21B is an exploded perspective view of the heat exchanger.

FIG. 22 is an enlarged plan view of a part of the heat exchanger viewed from the axial direction.

FIG. 23 is a schematic longitudinal sectional view of the radiator body and the heat exchanger.

FIG. 24 is an enlarged plan view of a part of the radiator according to the ninth embodiment of the present invention as viewed from the axial direction.

FIG. 25A is a cross-sectional view before the heat exchanger of the radiator is inserted from the introduction member side. ·

FIG. 25B is a cross-sectional view after the insertion.

FIG. 26 is a plan view of a radiator according to a tenth embodiment of the present invention.

FIG. 27 is a plan view of the heat exchanger of the radiator.

FIG. 28 is a plan view of a cylindrical main body.

FIG. 29 is a schematic cross-sectional view of a conventional free piston type Stirling refrigerator. FIG. 30 is an external perspective view of a radiator that is a conventional heat exchanger body.

FIG. 31 is an enlarged plan view of a part of a conventional heat exchanger as viewed from the axial direction. FIG. 32 is an enlarged plan view of a part of another conventional heat exchanger viewed from the axial direction. BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, embodiments of the present invention will be described with reference to the drawings. Members having the same names as those of the prior art shown in FIGS. 29 to 32 are denoted by the same reference numerals. In each embodiment, only the radiator 4 and its heat exchanger 42 will be described, but the configuration, selection of material for the members, and design changes also apply to the heat sink 2 and its heat exchanger 22. it can. Therefore, unless otherwise specified, the radiator 4 and the heat exchanger 42 may be replaced with the heat absorber 2 and the heat exchanger 22 in the description.

A first embodiment of the present invention will be described. FIG. 1 is an external perspective view of a radiator 4 which is a heat exchanger body of the present embodiment. FIG. 2A is an external perspective view showing the heat exchanger 42 of the radiator 4, and FIG. 2B is an exploded perspective view thereof. FIG. 3 is an enlarged plan view of a part of the heat sink seen from the axial direction. This heat exchanger 42 comprises an annular corrugated fin 4 21 and an inner ring-shaped member 4 22. The annular corrugated fins 4 21 are formed by forming a corrugated thin plate into a cylindrical shape so that each groove 4 21 a is parallel to the axial direction. The inner ring-shaped member 422 is a cylindrical body made of a material having good thermal conductivity.

First, a method for producing the annular korgutfin 421 used in the present embodiment will be described. 6A to 6C show a manufacturing procedure of the annular corrugated fin '421, FIG. 6A is a plan view showing a linear corrugated fin 420, and FIG. FIG. 6C is an enlarged plan view showing a state where the corrugated fins 420 are rounded and both ends are brought close to each other, and FIG. 6C is an enlarged plan view showing the completed annular corrugated fins 42 1.

As shown in FIG. 6A, one end of a linear corrugated fin 420 that is continuously connected to a V-shaped cross-sectional groove 420e is a V-shaped groove 420a, and the other end is The inverted V-shaped groove is 420 b. In addition,? The length 4 2 0 c of the end of the groove 4 2 0 a and the length 1 of the end 4 2 0 d of the groove 4 2 0 b are both the top 4 2 0 f and the top 4 2 of the groove 4 2 0 e between them. It is machined shorter than the length L of the hypotenuse between 0 f.

Then, the straight corrugated fins 420 are bent in the directions of the arrows F1 and F2 in FIG. 6A to form a cylindrical shape, and as shown in FIG. 6B, the end side 420c and the end side 420d are formed. 6c, and their end sides 420c and 420d are hooked together as shown in Fig. 6C to form an annular corrugated fin 421. As a result, the annular corrugated fins 421, 21 caught in an attempt to return to the original linear state, are pulled together by the ends 4200c, 420d, and the annular corrugated fins 421 are formed into an annular shape. Will be maintained. 4 2 1d is the connection.

As shown in FIG. 2A and FIG. 5, an inner ring-shaped member 422 is provided around the inner periphery of the annular corrugated fin 421 with the shafts of the ring (the shaft of the annular corrugated fin 421 and the ring-shaped member). 4 2 2 axes) are concentric. Here, the diameter of the circle (the inner diameter of the annular corrugated fin 4 21) formed by smoothly connecting the bottoms 4 2 1 b of the annular corrugated fins 4 21 and the outer diameter of the inner ring-shaped member 4 2 2 Is almost equal to

The annular corrugated fin 42 1 and the inner ring-shaped member 422 are joined by an annular brazing material 13. That is, as shown in Fig. 2B, the annular corrugated fin When the mouthpiece 13 is heated by placing the mouthpiece 13 on the portion where the inner ring-shaped member 4 2 2 comes into contact with the inner ring-shaped member 4, the melted mouthpiece 1 3 will follow the bottom 4 2 1 b of the annular corrugated fin 4 2 1 Down.

As a result, as shown in FIG. 3, the brazing material 13 spreads almost uniformly to the portion where the annular corrugated fins 4 21 and the inner ring-shaped member 4 2 2 come into contact. Then, as the brazing material 13 is hardened, the annular corrugated fins 42 1 and the inner ring-shaped members 42 2 are joined and integrated. Although brazing has been described here, soldering may also be performed.

The heat exchanger 42 described above is inserted into the main body 41 shown in FIG. The configuration for inserting the heat exchanger 42 into the main body 41 is as follows. That is, as shown in FIG. 4 which is a schematic cross-sectional view of the main body 41 and the heat exchanger 42, both ends of the main body 41 are tapered so that the wall thickness becomes thinner toward the end along the axial direction. (Taper portion _41a ).

The outer diameter of the heat exchanger 42 (the outer diameter of the annular corrugated fin 42 1) R 1 (= φ B) is the maximum inner diameter R 2 (= φ Β + α) at both end surfaces of the main body 41. And slightly larger than the inner diameter R 3 (= φ Β -α) in the axially inner side of the tapered portion 41a.

Therefore, when the heat exchanger 42 is inserted from the end of the main body 41, the heat exchanger 42 can be easily inserted at first with a small force. Then, since the inner diameter of the main body 41 gradually decreases and finally becomes smaller than the outer diameter R 1 of the heat exchanger 42, the heat exchanger 42 is inserted while gradually applying a large force. . In this way, the heat exchanger 42 can be easily inserted into the main body 41.

Here, since each bottom 4 2 1 b of the annular corrugated fin 4 2 1 is set up on the inner ring-shaped member 4 2 2, it is stored in the main body 4 1 having an inner diameter R 3 smaller than the outer diameter R 1. The formed annular corrugated fins 42 1 are in a state where the respective grooves 4 21 a are expanded, and an elastic force is generated radially outward.

Since the annular corrugated fin 42 1 has an outer diameter R 1 and a depth of each groove 4 21 a which is constant in the axial direction, the heat exchanger 42 is formed on the inner periphery of the main body 41 by the elastic force. It is uniformly pressed against the surface and fixed in position. At this time, the annular corrugated fins 4 2 1 And the inner ring-shaped member 4 2 2 are firmly fixed and do not deform.

As described above, in this embodiment, the heat exchanger 42 can be fixed at an appropriate position in the main body 41 without using an adhesive or solder, so that the process is simplified and the production cost is reduced. it can. Also, the heat exchange performance of the heat exchanger body is stabilized.

Further, when the annular corrugated fin 42 1 is damaged, the heat exchanger 42 can be pulled out from the main body 41 and taken out. Therefore, since it can be easily replaced as needed, the problem of economical burden on the user and the problem of recycling at the time of repair can be solved.

Furthermore, since the heat exchanger 42 used in the present embodiment integrates the annular corrugated fin 4 21 and the inner ring-shaped member 4 22 with brazing, soldering or the like, the heat exchanger 42 is configured separately. Also show good thermal conductivity. Therefore, the heat exchange efficiency is improved.

Next, a second embodiment of the present invention will be described. FIG. 7 is an enlarged plan view of the radiator 4 according to the present embodiment as viewed from the axial direction. The radiator 4 of the present embodiment is, like the first embodiment, a heat exchanger 4 comprising an annular corrugated fin 42 1 and an inner ring-shaped member 4 22 attached to the inside thereof. 2 and a cylindrical main body 4 1 on which the heat exchanger 42 is mounted.

First, a method for producing the cyclic corgefin 421 used in the present embodiment will be described. 8A to 8C show a manufacturing procedure of the cyclic corrugated fin 421, FIG. 8A is a plan view showing the linear corrugated fin 420, and FIG. 8B is a linear corrugated fin 420. FIG. 8C is an enlarged plan view showing a state where both ends are brought closer by rounding 420, and FIG. 8C is an enlarged plan view showing a part of the completed annular corrugated fin 421.

As shown in FIG. 8A, one end of a linear corrugated fin 420 in which V-shaped grooves 420e are continuously connected is a V-shaped groove 420a, and the other end is a V-shaped groove 420a. The inverted V-shaped groove is 420 b. In addition, the length L 2 of the edge 4 220 c of the groove 420 a and the edge 420 d of the groove 420 b is the same as the top portion 420 f of the groove 420 e therebetween. It is machined shorter than the length L of the hypotenuse between the tops 420 f.

Then, it is bent in the directions of arrows F l and F 2 in FIG. 20 is rounded into a cylindrical shape, and a part of the surface of the end side 420c and the end side 420d approached as shown in Fig. By joining, a circular corrugated fin 421 as shown in FIG. 8C is formed. 4 2 1 e is the connection or weld.

As shown in FIGS. 2A and 7, an inner ring-shaped member 422 is in contact with the inner periphery of the annular corrugated fin 421 so that their axes are concentric. Here, the diameter of the circle (inner diameter of the annular corrugated fin 42 1) formed by smoothly connecting the bottoms 4 2 1 b of the annular corrugated fin 4 21 and the outer diameter of the inner ring-shaped member 4 2 2 It is almost equal to the diameter.

The annular corrugated fins 4 21 and the inner ring-shaped members 4 2 2 are joined by an annular brazing material 13. That is, as shown in FIG. 2B, when the mouth material 13 is placed at a portion where the annular corrugated fin 42 1 and the inner ring-shaped member 42 2 are in contact with each other and ripened, the melted mouth material 13 becomes It flows down along the bottom 4 2 1 b of the annular corrugated fin 4 2 1.

As a result, as shown in FIG. 3, the brazing material 13 spreads substantially uniformly around the portion where the annular corrugated fins 4 21 and the inner ring-shaped members 4 2 2 are in contact. When the brazing material 13 is hardened, the annular corrugated fin 42 1 and the inner ring-shaped member 42 2 are joined and integrated. Although brazing has been described here, soldering may also be performed.

The above-described heat exchanger 42 is inserted into the main body 41 shown in FIG. The configuration for introducing the heat exchanger 42 into the main body 41 is as follows. That is, as shown in FIG. 4 which is a schematic cross-sectional view of the main body 41 and the heat exchanger 42, both ends of the main body 41 are tapered so that the wall thickness becomes thinner toward the end along the axial direction. It is formed (tapered portion 41a).

The outer diameter of the heat exchanger 42 (the outer diameter of the annular corrugated fins 42 1) R Ι (= φ Β) is calculated from the maximum inner diameter R 2 (= φ Β + α) at both end surfaces of the main body 41. Is slightly smaller and slightly larger than the inner diameter R 3 (= ψ Β _{-α 2} ) on the inner side in the axial direction than the tapered portion 41a.

Therefore, when this heat exchanger 42 is inserted from the end of the main body 41, it is initially small. The heat exchanger 42 can be easily inserted with a small force. Then, since the inner diameter of the main body 41 gradually decreases and finally becomes smaller than the outer diameter R1 of the heat exchanger 42, the heat exchanger 42 is inserted while gradually applying a large force. Go. In this way, the heat exchanger 42 can be easily inserted into the main body 41.

Here, since each bottom portion 4 21 b of the annular corrugated fin 4 21 is fixed to the inner ring-shaped member 4 22, the main body 4 1 having an inner diameter R 3 smaller than its outer diameter R 1 is formed. The stored corrugated fins 4 2 1 are in a state where the grooves 4 2 1 a are expanded and elastic force is generated radially outward.

Since the annular corrugated fins 42 1 have an outer diameter R 1 and the depth of each groove 4 21 a are constant in the axial direction, the mature exchanger 42 is formed on the inner periphery of the main body 41 by the elastic force. It is uniformly pressed against the surface and fixed in position. At this time, the annular corrugated fin 42 1 and the inner ring-shaped member 42 2 are firmly fixed and do not deform.

As described above, in this embodiment, the heat exchanger 42 can be fixed at an appropriate position in the main body 41 without using an adhesive or solder, thereby simplifying the process and achieving a reduction in manufacturing cost. it can. Also, the heat exchange performance of the heat exchanger body is stabilized.

Further, the heat exchanger 42 used in the present embodiment is formed separately from the annular corrugated fin 42 1 by integrating the inner ring-shaped member 42 2 with solder or solder. It shows better thermal conductivity than Therefore, the heat exchange efficiency is improved.

Next, a third embodiment of the present invention will be described. FIG. 9 is a plan view of a part of the radiator 4 according to the present embodiment as viewed from the axial direction. The radiator 4 of the present embodiment includes a heat exchanger 42 including an annular corrugated fin 42 1 and an inner ring-shaped member 42 2 attached to the inside thereof, similarly to the first embodiment. And a cylindrical main body 41 on which the heat exchanger 42 is mounted.

First, a method of manufacturing the annular corrugated fin 421 used in the present embodiment will be described. I will tell. 10A to 10B show a manufacturing procedure of the annular corrugated fin 421, FIG. 10A is a plan view showing a linear corrugated fin 420, and FIG. FIG. 10C is an enlarged plan view showing a state where the straight corrugated fins 420 are rounded and both ends are brought close to each other, and FIG. 10C is an enlarged plan view showing a part of the completed annular corrugated fins 42 1.

As shown in Fig. 10A, one end of a linear colgate fin 420 in which V-shaped cross-sectional grooves 420e are continuously connected is a V-shaped groove 420a, and the other end is The inverted V-shaped groove is 420 b. In addition, the length L 3 of the edge 4 20 c of the groove 4 20 a and the edge 4 2 0 d of the groove 4 20 b are both equal to the top 4 2 0 f of the groove 4 2 0 e therebetween. It is machined shorter than the length L of the hypotenuse between the tops 420 f.

Then, bend in the directions of arrows Fl and F2 in Fig. 10A, and straighten them so that the edges 4200c and 4200d that have been coated on the surface with an adhesive 16 such as an instant adhesive in advance. The colgate fins 420 are rounded into a cylindrical shape (Fig. 10B), and the end surfaces 420c and the application surface of the adhesive 16 at the end edges 420d are brought into contact with each other and held for a while. To form an annular korgut fin 421 as shown in FIG. 10C. 4 2 1 f is the bonded portion.

As shown in FIG. 2A and FIG. 9, an inner ring-shaped member 422 is in contact with the inner periphery of the annular corrugated fin 421 such that their axes are concentric. Here, the diameter of the circle (the inner diameter of the annular corrugated fin 42 1) formed by smoothly connecting the bottoms 4 2 1 b of the annular corrugated fin 4 21 and the outer diameter of the inner ring-shaped member 4 2 2 Is almost equal to

The annular corrugated fins 4 21 and the inner ring-shaped members 4 2 2 are joined by an annular brazing material 13. That is, as shown in FIG. 2B, when the mouthpiece 13 is placed on the portion where the annular corrugated fin 42 1 and the inner ring-shaped member 42 2 are in contact with each other and heated, the melted mouthpiece 13 becomes annular. It flows down along the bottom 4 2 1b of the corge tofin 4 2 1.

As a result, as shown in FIG. 3, the brazing material 13 spreads almost uniformly to the portion where the annular corrugated fins 4 21 and the inner ring-shaped member 4 2 2 come into contact. When the brazing material 13 hardens, the annular corrugated fins 42 1 and the inner ring-shaped members 4 2 2 And are integrated. Although brazing has been described here, soldering may also be performed.

The above-described heat exchanger 42 is inserted into the main body 41 shown in FIG. The configuration for introducing the heat exchanger 42 into the main body 41 is as follows. That is, as shown in FIG. 4 which is a schematic sectional view of the main body 41 and the heat exchanger 42, both ends of the main body 41 are tapered so that the wall thickness becomes thinner toward the end along the axial direction. Formed (tapered part 4 1 a) ₀

The outer diameter of the heat exchanger 42 (the outer diameter of the annular corrugated fin 42 1) R 1 (= φ B) is slightly smaller than the maximum inner diameter R + at both end faces of the main body 41. In addition, the inner diameter is slightly larger than the inner diameter R 3 (= φΒ−α ₂ ) on the inner side in the axial direction than the tapered portion 41 a.

Therefore, when the heat exchanger 42 is inserted from the end of the main body 41, the heat exchanger 42 can be easily inserted at first with a small force. Then, the inner diameter of the main body 41 gradually decreases, and eventually becomes smaller than the outer diameter R 1 of the heat exchanger 42, so that the heat exchanger 42 is inserted while gradually applying a large force. . In this way, the heat exchanger 42 can be easily inserted into the main body 41.

Here, since the bottoms 4 2 1 b of the annular corrugated fins 4 2 1 are fixed to the inner ring-shaped member 4 2 2, they are housed in the main body 4 1 having an inner diameter R 3 smaller than the outer diameter R 1. The formed annular corrugated fins 42 1 are in a state where the respective grooves 4 21 a are expanded, and an elastic force is generated radially outward.

Since the annular corrugated fin 42 1 has an outer diameter R 1 and a depth of each groove 4 21 a which is constant in the axial direction, the heat exchanger 42 is formed on the inner periphery of the main body 41 by the elastic force. It is uniformly pressed against the surface and fixed in position. At this time, the annular corrugated fins 4 21 and the inner ring-shaped members 4 2 2 are firmly fixed and do not deform.

When the corrugated fins 42 1 are damaged, the heat exchanger 42 can be pulled out from the main body 41 and taken out. Therefore, it can be easily replaced if necessary. It can solve the problem of economical burden on the user during repair and recycling.

Next, a fourth embodiment of the present invention will be described. FIG. 11 is a plan view of a part of the radiator 4 according to the present embodiment as viewed from the axial direction. The radiator 4 of the present embodiment is, similarly to the first embodiment, a heat exchanger 4 composed of an annular corrugated fin 4 21 and an inner ring-shaped member 4 22 attached to the inside thereof. 2 and a cylindrical main body 4 1 on which the heat exchanger 42 is mounted.

First, a method of manufacturing the annular corrugated fin 421 used in the present embodiment will be described. FIGS. 12A to 12C show the manufacturing procedure of the annular corrugated fins 421, FIG. 12A is a plan view showing the linear corrugated fins 420, and FIG. FIG. 12C is an enlarged plan view showing a state where the straight corrugated fins 420 are rounded and both ends are brought close to each other, and FIG. 12C is an enlarged plan view showing a part of the completed annular corrugated fins 42 1.

As shown in Fig. 12A, one end of a linear colgate fin 420 that continuously connects V-shaped grooves 420e is a V-shaped groove 420a, and the other end is The inverted V-shaped groove is 420 b. In addition, both the length L 4 of the edge 4 20 c of the groove 4 20 a and the edge 4 20 d of the groove 4 20 b are the same as the top 4 2 0 f of the groove 4 2 0 e therebetween. It is machined shorter than the length L of the hypotenuse between the tops 420 f.

Then, bend in the directions of arrows Fl and F2 in Fig. 12A, and corrugate the ends so that paste-like solder 17 is uniformly applied on the surface in advance. (See Fig. 12B). Solder by contacting the end faces 420c with the applied surface of solder 17 on end sides 420d and heating for a while. Form an annular corrugated fin 4 2 1 such as 1 2 C. 42lg is the braze or weld.

As shown in Fig. 2A and Fig. 11, the inner periphery of the annular corrugated fin 4 21 The ring-shaped members 422 are in contact with each other so that their axes are concentric. Here, the diameter of the circle (the inner diameter of the annular corrugated fin 42 1) formed by smoothly connecting the bottoms 4 2 1 b of the annular corrugated fins 4 21 and the outer diameter of the inner ring-shaped member 4 2 2 Is almost equal to

The annular corrugated fins 42 1 and the inner ring-shaped member 422 are joined by an annular brazing material 13. That is, as shown in FIG. 2B, when the mouthpiece 13 is placed on the portion where the annular corrugated fin 42 1 and the inner ring-shaped member 42 2 are in contact and heated, the melted mouthpiece 13 becomes It flows down along the bottom city 4 2 1b of the circular corrugated fin 4 2 1.

As a result, as shown in FIG. 3, the brazing material 13 spreads substantially uniformly around the portion where the annular corrugated fins 4 21 and the inner ring-shaped members 4 2 2 are in contact. Then, as the brazing material 13 is hardened, the annular corrugated fin 42 1 and the inner ring-shaped member 42 2 are joined and integrated. Although brazing has been described here, soldering may also be performed.

The outer diameter of the heat exchanger 42 (the outer diameter of the annular corrugated fin 42 1) R 1 (= φ B) is the maximum inner diameter R 2 (= φ Β + α) at both end faces of the main body 41. Are also slightly smaller and slightly larger than the inner diameter R 3 (= φΒ−α ₂ ) on the inner side in the axial direction than the tapered portion 41a.

Therefore, when the heat exchanger 42 is inserted from the end of the main body 41, the heat exchanger 42 can be easily inserted at first with a small force. Then, since the inner diameter of the main body 41 gradually decreases and finally becomes smaller than the outer diameter R1 of the heat exchanger 42, the heat exchanger 42 is inserted while gradually applying a large force. Go. In this way, the heat exchanger 42 can be easily inserted into the main body 41.

Here, each bottom 4 2 1 b of the annular corrugated fin 4 2 1 is an inner ring-shaped member. Since it is fixed to 4 2 2, the annular corrugated fin 4 2 1 housed in the main body 4 1 with an inner diameter R 3 smaller than its outer diameter R 1 is in a state where each groove 4 2 1 a is expanded. And an elastic force is generated radially outward.

Since the outer diameter R 1 and the depth of each groove 4 21 a of the annular corrugated fin 42 1 are constant in the axial direction, the heat exchanger 42 is attached to the main body 41 by the above-mentioned natural force. It is evenly pressed against the inner peripheral surface and fixed in position. At this time, the annular corrugated fins 4 21 and the inner ring-shaped members 4 2 2 are firmly fixed and do not deform.

Further, since the heat exchanger 42 used in the present embodiment integrates the annular corrugated fin 42 1 and the inner ring-shaped member 42 2 with a mouth or solder, the heat exchanger 42 is configured separately. It shows better conductivity than it does. Therefore, the heat exchange efficiency is improved.

Next, a fifth embodiment of the present invention will be described. FIG. 13 is a plan view of a part of the radiator 4 according to the present embodiment as viewed from the axial direction. The radiator 4 of the present embodiment is, similarly to the first embodiment, a heat exchanger 4 2 composed of an annular corrugated fin 4 21 and an inner ring-shaped member 4 2 2 brazed inside thereof. And a cylindrical main body 41 to which the heat exchanger 42 is attached.

First, a method of manufacturing the annular corrugated fin 421 used in the present embodiment will be described. FIGS. 14A to 14C show a manufacturing procedure of the annular corrugated fins 421, FIG. 14A is a plan view showing the linear corrugated fins 420, and FIG. FIG. 14C is an enlarged plan view showing a state in which the corrugated fins 420 are rounded and both ends are brought closer, and FIG. 14C is an enlarged plan view showing a part of the completed annular corrugated fins 42. As shown in Fig. 14A, one end and the other end of the linear colgate fin 420 where the V-shaped cross-sectional grooves 420e are continuously connected are inverted V-shaped grooves 420b. ing. The length L 5 of both ends 4 2 0 c and 4 2 0 d of the grooves 4 2 0 b at both ends is the same as the top 4 2 0 f of the grooves 4 2 0 e between them. It is shorter than the length L of the hypotenuse between the tops 420 f.

Then, bend in the directions of arrows F1 and F2 in Fig. 14A, and round the straight corrugated fin 420 into a cylindrical shape so that the edges 420c and 420d are aligned (Fig. 14 B), the end side 420c and the end side 420d are held in a state where their surfaces are in contact with each other over the entire surface, and are connected by a joint member 18 having a U-shaped cross section made of a highly elastic material. Thus, an annular corrugated fin 421 as shown in FIG. 14C is formed.

As shown in FIGS. 2A and 13, an inner ring-shaped member 42 is in contact with the inner periphery of the annular corrugated fin 42 1 so that their axes are concentric. Here, the diameter of the circle (the inner diameter of the annular corrugated fin 42 1) formed by smoothly connecting the bottoms 4 2 1 b of the annular corrugated fins 4 21 and the outer diameter of the inner ring-shaped member 4 2 2 Is almost equal to

The annular corrugated fins 4 21 and the inner ring-shaped members 4 2 2 are joined by an annular brazing material 13. That is, as shown in FIG. 2B, when the mouthpiece 13 is placed on the portion where the annular corrugated fin 42 1 and the inner ring-shaped member 42 2 are in contact with each other and heated, the melted mouthpiece 13 becomes annular. It flows down along the bottom 4 2 1b of the corrugated fin 4 2 1.

As a result, as shown in FIG. 3, the brazing material 13 spreads substantially uniformly around the portion where the annular corrugated fins 4 21 and the inner ring-shaped members 4 2 2 are in contact. Then, as the brazing material 13 is hardened, the annular korgut fin 42 1 and the inner ring-shaped member 42 2 are joined and integrated. Although brazing has been described here, soldering may also be performed.

The above-described heat exchanger 42 is inserted into the main body 41 shown in FIG. The configuration for introducing the heat exchanger 42 into the main body 41 is as follows. That is, as shown in FIG. 4 which is a schematic cross-sectional view of the main body 41 and the heat exchanger 42, both ends of the main body 41 are formed so that the wall thickness becomes thinner toward the end along the axial direction. A taper is formed (taper portion 41a).

The outer diameter of the heat exchanger 42 (the outer diameter of the annular corrugated fin 42 1) R 1 (= ψ B) is the maximum inner diameter R 2 (= φ Β + α) at both end faces of the main body 41. It is configured - (οί ₂ = φ Β) heavily on Mowazu slightly small and the inner diameter R 3 of the inside in the axial direction than the tapered portion 4 1 a also.

Here, since each bottom 4 2 1 b of the annular corrugated fin 4 2 1 is fixed to the inner ring-shaped member 4 2 2, it is stored in the main body 4 1 having an inner diameter R 3 smaller than its outer diameter R 1. The annular corrugated fins 4 21 are in a state where the respective grooves 4 2 1 a are expanded, and an elastic force is generated radially outward.

Since the annular corrugated fins 42 1 have an outer diameter R 1 and the depth of each groove 4 21 a are constant in the axial direction, the heat exchanger 42 is formed on the inner periphery of the main body 41 by the elastic force. It is uniformly pressed against the surface and fixed in position. At this time, the annular corrugated fins 4 21 and the inner ring-shaped members 4 2 2 are firmly fixed and do not deform.

When the annular corrugated fin 42 1 is damaged, the heat exchanger 42 can be pulled out from the main body 41 and taken out. Therefore, since it can be easily replaced as needed, the economic burden on the user at the time of repair and the problem of recycling can be solved.

Further, since the heat exchanger 42 used in the present embodiment integrates the annular corrugated fin 42 1 and the inner ring-shaped member 42 2 with a mouth or solder, the heat exchanger 42 is configured separately. It shows better thermal conductivity than it does. Therefore, the heat exchange efficiency is improved. Next, a sixth embodiment of the present invention will be described. FIG. 15 is a plan view of a part of the radiator 4 according to the present embodiment viewed from the axial direction. The radiator 4 of the present embodiment is, similarly to the first embodiment, a heat exchanger 4 composed of an annular corrugated fin 42 1 and an inner ring-shaped member 4 22 attached to the inside thereof. 2 and a cylindrical main body 4 1 on which the heat exchanger 42 is mounted.

First, a method of manufacturing the annular corrugated fin 421 used in the present embodiment will be described. FIG. 16 shows the manufacturing procedure of the annular corrugated fins 421, FIG. 16A is a plan view showing the linear corrugated fins 420, and FIG. FIG. 16C is an enlarged plan view showing a state in which the both ends are brought close together, FIG. 16C is an enlarged plan view showing the completed annular corge tofin 421, and FIG. It is a perspective view of a part.

As shown in Fig. 16A, one end and the other end of the linear colgate fin 420 in which the V-shaped cross-sectional grooves 420e are continuously connected are inverted V-shaped grooves 420b. ing. The length L 6 of both ends 4 2 0 c and 4 2 0 d of the grooves 4 2 0 b at both ends is the same as the top 4 2 0 f of the grooves 4 2 0 e between them. It is machined to be shorter than the length L of the hypotenuse between the tops 420 f. Also, as shown in FIG. 17, each of the side edges 420c and 420d has a straight corrugated fin 420 from one side 420g to the other side 420h and another side 420h. There is provided a slit 19 extending from one side to the 20 g side.

Then, bend in the directions of arrows F1 and F2 in Fig. 16A, and round the straight corrugated fin 420 into a cylindrical shape so that the end sides 420c and 420d are aligned (Fig. 1 6B), and furthermore, the edges 42 0c and 42 0d are so arranged that the slit 19 of the edge 420c and the slit 19 of the edge 420d fit alternately. By coupling, an annular corrugated fin 421 as shown in FIG. 16C is formed.

As shown in FIG. 2A and FIG. 15, an inner ring-shaped member 422 is in contact with the inner periphery of the vertical corrugated fin 421 so that their axes are concentric. Here, the diameter of the circle formed by smoothly connecting the bottoms 4 2 1 b of the 状 -shaped corrugated fins 4 2 1

(The inner diameter of the annular korgut fine 422) and the outer diameter of the inner ring-shaped member 422 are almost equal. The annular corrugated fins 4 21 and the inner ring-shaped members 4 2 2 are joined by an annular brazing material 13. That is, as shown in FIG. 2B, when the mouthpiece 13 is placed on a portion where the annular corrugated fin 42 1 and the inner ring-shaped member 42 2 are in contact and heated, the melted mouthpiece 13 becomes It flows down along the bottom 4 2 1 b of the annular corrugated fin 4 2 1.

The heat exchanger 42 described above is inserted into the main body 41 shown in FIG. The configuration for introducing the heat exchanger 42 into the main body 41 is as follows. That is, as shown in FIG. 4 which is a schematic sectional view of the main body 41 and the mature exchanger 42, both ends of the main body 41 are tapered so that the wall thickness becomes thinner toward the end along the axial direction. Formed (tapered part 4 1 a) ₀

The outer diameter of the heat exchanger 42 (the outer diameter of the annular corrugated fin 42 1) R 1 (= ψ B) is the maximum inner diameter R 2 (= φ Β + α) at both end faces of the main body 41. And slightly larger than the inner diameter R 3 (= φΒ−α ₂ ) in the axial direction inside the tapered portion 41a.

Therefore, when the heat exchanger 42 is inserted from the end of the main body 41, the heat exchanger 42 can be easily inserted at first with a small force. Then, since the inner diameter of the main body 41 gradually decreases, and eventually becomes smaller than the outer diameter R 1 of the heat exchanger 42, the heat exchanger 42 is inserted while gradually applying a large force. Go. In this way, the heat exchanger 42 can be easily inserted into the main body 41.

Here, since each bottom 4 2 1 b of the annular corrugated fin 4 2 1 is fixed to the inner ring-shaped member 4 2 2, it is stored in the main body 4 1 having an inner diameter R 3 smaller than its outer diameter R 1. The annular corrugated fins 421 are in a state in which the grooves 421 a are expanded, and an elastic force is generated radially outward.

The annular corrugated fin 4 21 has an outer diameter R 1 and a depth of each groove 4 21 a. Since it is constant in the axial direction, the heat exchanger 42 is uniformly pressed against the inner peripheral surface of the main body 41 and fixed in position by the elastic force. At this time, the annular corrugated fins 42 1 and the inner ring-shaped members 42 2 are firmly fixed and do not deform.

As described above, in this embodiment, the heat exchanger 42 can be fixed at an appropriate position in the main body 41 without using an adhesive or solder, so that the process is simplified and the production cost is reduced. it can. In addition, the heat exchange performance of the heat exchanger is stabilized.

Further, when the annular corrugated fin 42 1 is damaged, the heat exchanger 42 can be pulled out from the main body 41 and taken out. Therefore, since it can be easily replaced as needed, the economic burden on the user at the time of repair and the problem of recycling can be solved.

Further, since the heat exchanger 42 used in the present embodiment integrates the annular corrugated fin 42 1 and the inner ring-shaped member 42 2 with a mouth or solder, the heat exchanger 42 is configured separately. It shows better thermal conductivity than it does. Therefore, the heat exchange efficiency is improved. '

A seventh embodiment of the present invention will be described with reference to the drawings. FIG. 18 is a plan view of the radiator 4 according to the present embodiment as viewed from the axial direction. The radiator 4 of the present embodiment is, like the first embodiment, a heat exchanger 4 2 composed of an annular corrugated fin 4 21 and an inner ring-shaped member 4 22 attached to the inside thereof. And a cylindrical main body 41 to which the heat exchanger 42 is mounted.

First, a method for producing the annular korgutfin 421 used in the present embodiment will be described. FIG. 19A to FIG. 19C show a production procedure of the cyclic corrugated fins 421, FIG. 19A is a plan view showing a linear corrugated fin 420, and FIG. FIG. 19C is a plan view showing an annular corrugated fin 421 formed by rolling the corrugated fins 420 and bringing both ends close together, and FIG. 19C is a top view of the cylindrical main body 41.

As shown in FIG. 19A, one end and the other end of the linear colgate fin 420 in which the V-shaped groove 420 e continuously extends are inverted V-shaped grooves 420 b It has become. The length L 7 of both ends 4 2 0 c and 4 2 0 d of the grooves 4 2 0 b at both ends is the same as the term 4 2 0 f of the grooves 4 2 0 e between them. Length of the hypotenuse between the top 4 20 f and length L Well processed.

Then, bend in the directions of arrows F 1 and F 2 in FIG. 19A, and round the straight corrugated fin 420 into a cylindrical shape so that the end sides 420 c and 420 d are aligned. An annular corrugated fin 421 as shown in FIG. 19B is formed by holding a state in which the tips of 迈 420 c and the edges 420 d are in contact with each other. As a result, the distal ends of the side edges 420c and 420d are positioned more radially than the outer periphery of the annular corrugated fin 421 (the circumference of a circle formed by smoothly connecting the tops 4221c). Thus, a protruding portion 4 21 h protruding outside the frame is formed.

The inner diameter of the cylindrical body 41 is selected to be substantially equal to the outer diameter of the annular corrugated fin 42. Further, as shown in FIG. 19C, a concave portion 41 a that can be fitted to the protruding portion 421 h of the annular corrugated fin 421 is provided at one location on the inner surface of the outer heat exchanger 3 in the axial direction. It has been extended.

Then, the annular corrugated fins 42 1 are aligned with the center axis of the main body 41, and the projections 42 21 h are fitted into the concave portions 41 a of the main body and inserted from the axial direction. At this time, as shown in FIG. 1, the one end surface of the annular corrugated fin 42 1 is inserted until the open end of the main body 41 is aligned.

A force trying to return to the original linear corrugated fin 420 is applied to the protruding portion 4 21 h of the annular corrugated fin 4 21, but the protruding portion 4 2 1 h is in the recess 4 a. Since the movement is restricted, the annular corrugated fin 4 21 changes to a force that tries to spread in the radial direction. Therefore, since the annular corrugated fins 42 21 are spread and pressed against the inner surface of the main body 41, the annular corrugated fins 42 can be held at a predetermined position while maintaining the shape. '

On the other hand, the outer diameter of the cylindrical inner ring-shaped member 422 is selected to be substantially equal to the inner diameter of the annular corrugated fin 421 (diameter of a circle formed by smoothly connecting the grooves 2b). Then, the center of the inner ring-shaped member 422 is aligned with the center axis of the annular corrugated fin 421 in the main body 1 and inserted from the axial direction. Then, the heat exchanger 42 is mounted inside the main body 41 by attaching it to the contact portion between the inner periphery of the annular colgate fin 42 1 and the outer surface of the inner ring-shaped member 42 2 to be integrated. As a result, a radiator 4 as shown in FIG. 18 is obtained. Therefore, steps such as bonding and welding of the annular corrugated fins 42 1 to the main body 41 are omitted to improve productivity, and the annular corrugated fins 42 1 can be securely fixed by press-fitting. Since a uniform contact state is obtained over the entire circumference of 21, it is possible to stably provide the radiator 4 having excellent performance. Next, an eighth embodiment according to the present invention will be described. FIG. 20 is an external perspective view of a radiator 4 which is a heat exchanger body of the present embodiment. FIG. 21A is an external perspective view showing a heat exchanger 42 ′ incorporated in the radiator 4, and FIG. 21B is an exploded perspective view thereof.

The heat exchanger 42 'is composed of an annular corrugated fin 421, an outer ring-shaped member 42' and a heat exchanger. The annular corrugated fin 421 is manufactured by the procedure described in each of the first to seventh embodiments. The outer ring-shaped member 4 2 2 ′ is a cylindrical body made of a material having good thermal conductivity and elasticity.

As shown in FIG. 21A, an outer ring-shaped member 42 2 ′ is in contact with the outer periphery of the annular corrugated fin 42 1 so that their axes are concentric with each other. Here, the outer diameter of the annular corrugated fins 42 1 is substantially equal to the inner diameter of the outer ring-shaped member 42 2 ′. As shown in FIG. 22, the annular corrugated fin 42 1 and the outer ring-shaped member 42 2 ′ are similar to the annular corrugated fin 42 1 and the inner ring-shaped member 42 2 of the first embodiment. It is joined and fixed with brazing material 13 or solder.

The above-described heat exchanger 42 ′ is inserted into the main body 41 shown in FIG. 20 so that the axes are concentric with each other to form the radiator 4. The configuration for inserting the heat exchanger 42 into the main body 41 is as follows. That is, as shown in FIG. 23 which is a schematic cross-sectional view of the main body 41 and the heat exchanger 42 ′, both ends of the main body 41 are tapered in the same manner as in the first embodiment (tapered portion 4). 1 a) ₀

The outer diameter of the heat exchanger 4 2 ′ (the outer diameter of the outer ring-shaped member 4 2 2 ′) R Γ (= φ Β ′) is the maximum inner diameter R 2 ′ (= Slightly smaller than +-Β '+ α'), and the tapered part 41 and inner diameter is slightly smaller than the inner diameter 13 '. (= (& 5, -α ₂ ') It is largely configured.

Therefore, as in the first embodiment, the heat exchanger 42 'can be easily inserted into the main body 41 by the tapered portion 4la. In addition, the The heat exchanger 42 'is pressed against the inner peripheral surface of the main body 41 by an elastic force generated in the annular corrugated fin 42 and the outer ring-shaped member 42' and fixed in position. At this time, the annular corrugated fins 42 1 and the outer ring-shaped members 42 2 ′ are firmly fixed and do not deform.

As described above, also in the present embodiment, the heat exchanger 4 2 ′ can be fixed at an appropriate position in the main body 41 without using an adhesive or solder, and the main body 4 1 and the heat exchanger 4 2 ′ are different from each other. Since it is not fixed, it can be taken out freely. Further, since the annular corrugated fins 42 1 and the outer ring-shaped members 42 2 ′ are integrated, they show better thermal conductivity.

A _ninth embodiment of the present invention will be described with reference to the drawings. FIG. 24 is an enlarged plan view of a part of the radiator 4 according to the present embodiment viewed from the axial direction. Fig. 25 shows a part of the manufacturing procedure of the radiator 4. Fig. 25A is a cross-sectional view before the heat exchanger 42 is inserted from the introduction member 14 side. It is sectional drawing after insertion.

As shown in FIGS. 25A and 25B, the cylindrical main body 41 is fixed to the jig 15 together with the introduction member 14 so that the axial direction thereof is substantially horizontal. The introduction member 14 provided adjacent to the main body 41 has an outer diameter substantially equal to that of the main body 41, and the inner diameter is substantially equal to the inner diameter of the main body 41 at the joint portion, and increases as the distance from the joint portion increases It has a sectional shape of the inner surface having a tapered portion 14a.

Hereinafter, the manufacturing procedure of the radiator 4 according to the present embodiment will be described with reference to FIGS. 25A and 25B. As described in the first to sixth embodiments, the annular corrugated fins 421 are formed in an annular shape by rolling the linear corrugated fins 420 and fixing both ends. The annular corrugated fins 421 are formed of a highly flexible material which is easily deformed by an external force.

In advance, an inner ring-shaped member 4 22 selected to have an outer diameter slightly larger than the inner diameter is inserted into the annular corrugated fin 4 21 from the axial direction to produce a heat exchanger 42. . Then, as shown in FIG. 25A, the heat exchanger 42 is inserted axially from the open end of the introduction member 14. As a result, the annular corrugated fins 42 1 are pressed from the center to the outside by the inner ring-shaped member 42 2 in the radial direction, and are reduced from the portion having the larger inner diameter along the tapered portion 14 a of the introduction member 14. Gradually to the place It will be pushed into.

Then, as shown in FIG. 25B, the insertion is terminated when the one end surface of the annular corrugated fin 42 reaches the junction between the main body 41 and the introduction member 14. As a result, the top 4 21 c of the annular corrugated fin 42 1 rubs against the inner surface of the introduction member 14, and its shape is changed from an arc shape to a planar shape. The degree of this deformation increases as the hardness S of the material of the introduction member 14 and the hardness of the material of the annular corrugated fin 42 1 become greater. Thereby, as shown in FIG. 24, the contact area between the annular corrugated fins 4 21 and the inner surface of the main body 41 is increased. Therefore, the efficiency of heat transfer from the annular corrugated fin 42 1 to the main body 41 is improved, and the heat exchange performance of the radiator 4 is improved. A tenth embodiment of the present invention will be described with reference to the drawings. FIG. 26 is a plan view of a radiator 42 according to the present embodiment, FIG. 27 is a plan view of a heat exchanger 42, and FIG. 28 is a plan view of a cylindrical main body 41. .

On the outer periphery of the annular corrugated fin 42 1 ′, rounded convex portions 4 21 k are formed, and the adjacent convex portions 4 21 k are closely attached to each other and are arranged at equal intervals as a whole. In. On the other hand, the main body 41 is formed by pouring the molten metal into a mold and solidifying it. As shown in FIG. 28, a wavy concave part 41 m extending in the axial direction is formed on the entire inner surface of the main body. It is given at equal intervals. The concave portion 41 m is shaped so that the convex portion 421 k of the annular corrugated fin 42 1 ′ can be fitted.

As shown in FIG. 2A, a cylindrical inner ring-shaped member 42 2 having an outer diameter slightly equal to the inner diameter is inserted into the corrugated fin 4 21 ′ in advance, and the contact portion is formed. By brazing, a heat exchanger 42 as shown in FIG. 27 is prepared. Then, as shown in FIG. 4, the center of the heat exchanger 42 is aligned with the center axis of the main body 41 and inserted from the axial direction. At this time, as shown in FIG. 26, since the convex portion 4 2 1 k of the annular corrugated fin 4 2 1 ′ and the concave portion 4 1 m of the main body 4 1 fit together, the main body 4 1 of the heat exchanger 4 2 The radiator 4 whose position along the circumferential direction in 內 is reliably fixed can be obtained. Therefore, according to the present embodiment, the annular corrugated fin 4 2 1 ′ is firmly adhered to the inner surface of the main body 4 1, and a sufficient contact area is secured over the entire circumference of the annular corrugated fin 4 2 1 ′. A radiator 4 having excellent performance can be stably provided. Industrial applicability

As described above, the heat exchanger of the present invention does not need to be manually bonded to the main body, so that the productivity of the heat exchanger body can be improved and the production cost can be reduced. Moreover, the obtained heat exchanger body has little variation in quality and has stable heat exchange performance. In addition, the heat exchanger improves the heat conductivity by integrating the corrugated fin and the inner or outer ring-shaped member, thereby improving the heat exchange efficiency.

Further, since the position of the heat exchanger is fixed by pressing the heat exchanger against the main body of the heat exchanger body, the heat exchanger can be pulled out from the main body and taken out. Therefore, even if the corrugated fins are damaged and the quality of the heat exchanger deteriorates, the corrugated fins can be easily replaced as needed, making them very economical and suitable for recycling. . In particular, if the end of the main body of the heat exchanger body has a taper, even if the outer diameter of the heat exchanger is larger than the inner diameter of the main body, the heat exchanger can be smoothly inserted.

Also, there is no need to manually attach the annular corrugated fins to the inside of the tubular body by bonding or welding. Therefore, an improvement in the productivity of the heat effect gas is achieved. In addition, a uniform contact state is obtained over the entire circumference of the annular corrugated fin, so that a heat exchanger body having excellent performance can be stably supplied.

Claims

The scope of the claims

1. An annular corrugated fin in which a thin plate having a number of grooves formed by corrugating is formed into a cylindrical shape so that the grooves are parallel to the axial direction, and an inner ring-shaped member in contact with the inner periphery of the annular corrugated fin. A heat exchanger for a Stirling refrigerator characterized by being integrated.

2. In a heat exchanger body formed by inserting the heat exchanger for a Stirling refrigerator according to claim 1 into the hollow of a tubular main body, an inner diameter of the main body is smaller than an outer diameter of the heat exchanger. A heat exchanger body characterized by having a smaller size.

3. The heat exchanger body according to claim 2, wherein at least one end of the main body is tapered so that the wall thickness becomes thinner toward the end side along the axial direction. The maximum inner diameter of the main body was made larger than the outer diameter of the heat exchanger.

4. The heat exchanger body according to claim 2, wherein around the annular corrugated fin, corrugated convex portions are formed in close contact with each other and are arranged at equal intervals as a whole, and these convex portions are formed. In response to the above, the convex portion is fitted into the corrugated concave portion extending in the axial direction on the inner surface of the main body. ·

5. The heat exchanger body according to claim 2, wherein the annular corrugated fin is a linear corrugated fin in which an end of an inverted V-shaped groove at both ends is longer than an oblique side of a V-shaped groove therebetween. One tofin is rolled into a cylindrical shape, and the annular corrugated fins are prepared by holding the both end sides so that the surfaces are in contact with each other. The outer periphery of the annular corrugated fin formed at the tip of the both end sides is prepared. A radially projecting projection is attached to the inner surface of the body. It is designed to fit into the groove extending in the axial direction.

6. The method for manufacturing a heat exchanger body according to claim 2, wherein the tubular introduction member is tapered such that one end has substantially the same inner diameter as the main body and the wall thickness decreases toward the other end. A method for manufacturing a heat exchanger body, comprising: detachably attaching the one end to the main body, and inserting the heat exchanger for the Stirling refrigerator in the axial direction from the other end of the introduction member.

7. An annular corrugated fin in which a thin plate having a large number of grooves formed by corrugating is formed into a cylindrical shape so that the grooves are parallel to the axial direction, and an outer ring-shaped member in contact with the outer periphery of the annular corrugated fin. A heat exchanger for a Stirling refrigerator characterized by being integrated.

8. A heat exchanger body comprising the heat exchanger for a Stirling refrigerator according to claim 7 inserted into the hollow of a tubular main body, wherein an inner diameter of the main body is smaller than an outer diameter of the heat exchanger. A heat exchanger body characterized by having a smaller size.

9. The heat exchanger body according to claim 8, wherein at least one end of the main body is tapered so that the wall thickness becomes thinner toward the end along the axial direction. The maximum inner diameter of the main body was made larger than the outer diameter of the heat exchanger.

10. The heat exchanger for a Stirling refrigerator according to claim 1 or 7, wherein the annular corrugated fins are formed by rounding a linear corrugated fin in which V-shaped grooves are continuously connected, into a cylindrical shape, Engage the end of the V-shaped groove at one end with the end of the inverted V-shaped groove at the other end It is connected by doing.

11. The heat exchanger for a Stirling refrigerator according to claim 1 or 7, wherein the annular corrugated fins are formed by rolling a linear korgut fin in which V-shaped grooves are continuously connected into a cylindrical shape. One end of the V-shaped groove at one end and the end of the inverted V-shaped groove at the other end are connected to each other by spot welding.

12. The heat exchanger for a Stirling refrigerator according to claim 1 or 7, wherein the annular corrugated fins are formed by rolling a linear corrugated fin in which V-shaped grooves are continuously connected into a tubular shape. One end of the V-shaped groove at one end and the other end of the inverted V-shaped groove at the other end are connected to each other by bonding them to each other.

13. The heat exchanger for a Stirling refrigerator according to claim 1 or 7, wherein the annular corrugated fins are formed by rolling a linear corrugated fin in which V-shaped grooves are continuously connected into a cylindrical shape. One end of the V-shaped groove at one end and the other end of the inverted V-shaped groove at the other end are connected to each other by bonding the surfaces to each other.

14. The heat exchanger for a Stirling refrigerator according to claim 1 or 7, wherein the annular corrugated fin is formed by rolling a linear corrugated fin in which V-shaped grooves are continuously connected into a cylindrical shape. The ends of the inverted V-shaped grooves at both ends are held so that their surfaces are in contact with each other, and a joint member having a U-shaped cross section is attached to the tip of the contact portion to connect the ends. Consisting of

15. The heat exchanger for a Stirling refrigerator according to claim 1 or 7, wherein the annular corrugated fin is a tubular corrugated fin in which a V-shaped groove continuously extends. A rounded, slit formed on one side of the inverted V-shaped groove at one end from one side of the linear corrugated fin to the other side, and an inverted V-shaped groove at the other end of the linear corrugated fin. A slit formed on the other side of the linear corrugated fin from one side to the other side is fitted to each other to be connected to each other.