KR20030028830A - Heat exchanger for stirling refrigerating machine, heat exchanger body, and method of manufacturing heat exchanger body - Google Patents

Abstract

A heat exchanger for a sterling refrigerator is formed by integrating an annular corrugation 한 formed into a cylindrical shape in which a plurality of grooves are formed by a pleating process so that the grooves are parallel to the axial direction, and an inner ring-shaped member in contact with the inner circumference of the annular pleat 휜. To make. The heat exchanger for the sterling refrigerator or the heat absorber is obtained by inserting the heat exchanger into the hollow of the main body.

Description

HEAT EXCHANGER FOR STIRLING REFRIGERATING MACHINE, HEAT EXCHANGER BODY, AND METHOD OF MANUFACTURING HEAT EXCHANGER BODY}

First, a general configuration of a free piston type sterling refrigerator using a sterling engine will be described. Fig. 29 is a schematic side view of the free piston type Stirling refrigerator. In the cylinder 1, the heat absorber 2 which becomes a low temperature part, the regenerator 3, and the heat radiator 4 which becomes a high temperature part are accommodated in this order. The heat absorber 2 and the radiator 4 are both heat exchangers formed by attaching the heat exchangers 22 and 42 to the inner circumferential surface of one end side of the tubular bodies 21 and 41, and each heat exchanger 22 and 42. Is adjacent to the regenerator 3 in the cylinder 1.

In the cylinder 1, a displacer 6 fixed to one end of the displacer rod 5 and a piston 7 through which the displacer rod 5 penetrate are arranged. In addition, the other end of the displacer 5 is connected to the spring 8. In the cylinder 1, an expansion space 9 is formed inside the heat sink 2 by these displacers 6 and a piston 7, and a compression space 1 is formed inside the heat sink 4. have. These expansion spaces 9 and compression spaces 10 communicate with each other by the regenerator 3 to form a closed circuit.

The operation of this free piston type sterling refrigerator will be described. The piston 7 reciprocates at predetermined cycles in the axial direction of the cylinder 1 by external power such as a linear motor (not shown). In addition, a working gas such as helium is sealed in the compression space 10 in advance.

When the working gas in the compression space 10 is compressed by the movement of the piston 7, the working gas flows into the expansion space 9 through the regenerator 3 via the heat exchanger 42 of the radiator 4 ( In the drawings, dashed arrows A). At this time, the working gas which has generated heat by compression is heat exchanged with the outside air in the heat exchanger 42 to release heat, and passes through the regenerator 3 to receive the cold heat previously accumulated in the regenerator 3. It is precooled.

When the working gas enters the expansion space 9, the displacer 6 is pressurized in the right direction against the spring 8 so that the working gas expands and cools. And, when the working gas expands to some extent, the displacer 6 is returned to the opposite direction by the return force of the spring 8.

Thereby, the working gas in the expansion space 9 moves back through the regenerator 3 to the compression space 10 via the heat exchanger 22 of the heat absorber 2 (solid arrow A 'in the figure). At this time, the working gas is heat exchanged with the outside air in the heat exchanger 22 to absorb heat, and passes through the regenerator 3 to receive the heat accumulated in the regenerator 3 and is preheated. The working gas returned to the compression space 10 is again compressed by the piston 7.

By repeating such a series of cycles continuously, the cryogenic cold heat is taken out from the heat absorber 2. Here, it is preferable that the heat absorbing amount in the heat exchanger 22 of the heat absorber 2 and the heat dissipating amount in the heat exchanger 42 of the radiator 4 are larger. This is because the efficiency of precooling and preheating of the regenerator 3 with respect to the working gas is improved, so that the burden on the regenerator 3 can be reduced, and further, the improvement of the freezing performance of the sterling refrigerator can be achieved.

Next, the radiator 4 which is the high temperature side heat exchanger of the above-described sterling refrigerator will be described with reference to FIG. In addition, although only the radiator 4 and its heat exchanger 42 are described here, the heat absorber 2 and the heat exchanger 22 which are low temperature side heat exchanger bodies are the same structure.

As shown in Fig. 30, the heat exchanger 42 is an annular corrugated fin 421 in which a corrugated thin plate is formed in a cylindrical shape. A plurality of V-shaped grooves 421a extending linearly along the axial direction are formed at equal intervals, and are pleated.

Here, the part which protrudes in the center side of the main body 41 of the heat sink 4 is used as the bottom part 421b of each groove | channel 421a, and the part which protrudes in the side of the inner peripheral surface of the main body 41 is an adjacent groove | channel It is set as the top part 421c formed by 421a. The diameter of the circle (the outer diameter of the annular pleat fin 421) and the inner diameter of the main body 41 which are able to connect each top part 421c smoothly is substantially the same, and the main body 41 and the annular pleat fin 421 are mutually axial. It is arranged to be concentric.

The inner circumferential surface of the main body 41 and the top 421c of the annular corrugated fin 421 are firmly fixed by an adhesive or solder. Fig. 31 is an enlarged view of a main portion of the annular corrugated fin 421 viewed from the axial direction, and shows a state of being fixed with an adhesive agent. In this case, first, the adhesive 11 is spread out thinly on the inner circumferential surface of the main body 41, and an annular pleat fin 421 is inserted therein. And the adhesive agent 11 is dried in the state which hold | maintained the annular wrinkles 421 for a predetermined position for a while.

32 shows a state of fixing with solder. In the case of soldering, first, the annular corrugated fin 421 is inserted into the main body 41. Then, the solder 12 is applied to a portion where the inner circumferential surface of the main body 41 and the top portion 421c of the annular pleat fin 421 are in contact with or close to each other while holding the annular pleat fin 421 at a predetermined position. do.

However, in the above-mentioned conventional heat exchange gas, the fixing process by gluing or soldering is performed manually. Therefore, this process is very laborious and time-consuming, resulting in poor productivity and difficulty in reducing manufacturing costs. Moreover, the quality of a product, ie, heat exchange performance, tends to fluctuate, and there is a defect in the stability and reliability of the product.

In addition, if the annular wrinkle 기를 421 is damaged due to long-term use of the sterling freezer, it could be replaced by removing it. Therefore, there has been a problem in that it is a so-called recycling of the economic burden on the user at the time of repair and a resource in consideration of the global environment.

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger gas such as an absorber or a radiator provided in a Stirling refrigerator, and a method for producing the heat exchanger and the heat exchanger gas.

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

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

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

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

4 is a schematic longitudinal sectional view of the 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 straight wrinkle 휜.

Fig. 6B is an enlarged plan view showing a state in which both ends are rolled up by rolling straight wrinkles 휜.

Fig. 6C is an enlarged plan view showing a part of the completed annular pleat shock.

7 is an enlarged plan view of a part of the radiator according to the second embodiment of the present invention as seen from the axial direction.

Fig. 8A is a plan view showing a straight wrinkle 휜.

Fig. 8B is an enlarged plan view showing a state where both ends are rolled up by rolling straight wrinkles 휜.

Fig. 8C is an enlarged plan view showing a portion of the completed annular pleat shock.

9 is an enlarged plan view of a part of the radiator according to the third embodiment of the present invention as seen from the axial direction.

Fig. 10A is a plan view showing a straight wrinkle 휜.

Fig. 10B is an enlarged plan view showing a state in which both ends are rolled up by rolling straight wrinkles 휜.

Fig. 10C is an enlarged plan view showing a part of the completed annular pleat shock.

11 is an enlarged plan view of a part of the radiator according to the fourth embodiment of the present invention as seen from the axial direction.

Fig. 12A is a plan view showing the straight wrinkles 휜.

Fig. 12B is an enlarged plan view showing a state in which both ends are rolled up by rolling straight wrinkles 접근.

Fig. 12C is an enlarged plan view showing a portion of the completed annular pleat shock.

Fig. 13 is an enlarged plan view of a part of the heat sink according to the fifth embodiment of the present invention as seen from the axial direction.

Fig. 14A is a plan view showing the straight wrinkles 휜.

Fig. 14B is an enlarged plan view showing a state in which both ends are rolled up by rolling straight wrinkles 휜.

Fig. 14C is an enlarged plan view showing a part of the completed annular pleat shock.

Fig. 15 is an enlarged plan view of a part of the heat sink according to the sixth embodiment of the present invention as seen from the axial direction.

Fig. 16A is a plan view showing a straight wrinkle fold.

Fig. 16B is an enlarged plan view showing a state in which both ends are rolled up by rolling straight wrinkles 접근.

Fig. 16C is an enlarged plan view showing a part of the completed annular corrugation pin.

Fig. 17 is an enlarged perspective view showing the main part of Fig. 16B.

18 is an enlarged plan view of the radiator according to the seventh embodiment of the present invention as seen from the axial direction.

Fig. 19A is a plan view showing a straight wrinkle 휜.

Fig. 19B is a plan view showing the annular corrugated paper formed by rolling up the straight corrugated paper and contacting both ends thereof.

Fig. 19C is a top view of the cylindrical body.

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 the 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 portion of the heat exchanger viewed from the axial direction.

Fig. 23 is a schematic longitudinal sectional view of the main body and heat exchanger of the radiator;

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

Fig. 25A is a sectional view before insertion of the heat exchanger of the radiator to the introduction member side.

Fig. 25B is a sectional view after 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 a heat exchanger of the radiator.

Fig. 28 is a plan view of the cylindrical body.

29 is a cross-sectional schematic diagram of a conventional free piston type sterling refrigerator.

30 is an external perspective view of a heat sink that is a conventional heat exchange gas.

Fig. 31 is an enlarged plan view of a part of the heat exchanger of the prior art as seen from the axial direction.

32 is an enlarged plan view of a portion of a heat exchanger according to another conventional example viewed from the axial direction.

This invention is made | formed in order to solve the said subject. That is, the heat exchanger for the sterling refrigerator of the present invention has an annular pleat 한 formed in a cylindrical shape so that the grooves are parallel to the axial direction by a thin plate having a plurality of grooves formed therein, and an inner side which is in contact with the inner circumference of the annular pleat 휜. The ring member is integrated.

If these annular corrugations 휜 and the inner ring-shaped member are integrated, their contact area is increased and good thermal conductivity is displayed. In addition, the integration facilitates the handling of the heat exchanger, and also enables heat exchange repair. Therefore, it is very economical and rich in recycling. Moreover, what is necessary is just to perform a bonding means, for example, brazing and brazing.

The heat exchanger gas of the present invention is obtained by inserting the heat exchanger for sterling refrigerator into the hollow of the tubular body. In this case, if the inner diameter of the main body is made slightly smaller than the outer diameter of the heat exchanger, the heat exchanger can be attached to the main body by pressing without welding or welding. In addition, the taper may be easily inserted into at least one end of the main body so that the wall thickness becomes thinner toward the end side in the axial direction.

Further, in the case where the convex portions of the corrugated portions are in close contact with each other around the annular corrugations 늘어 and are arranged at equal intervals as a whole, and the concave portions of the corrugated portions are provided in the axial direction on the inner surface of the main body corresponding to the convex portions, By inserting the convex portion and the concave portion when inserting the 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, the end face of the inverted V-shaped grooves at both ends is rolled into a cylindrical shape having a straight pleat 휜 longer than the inclined side of the V-shaped groove therebetween, and the both ends are held so as to contact the surface with each other, It is possible to prevent the position of the heat exchanger in the main body from shifting in the circumferential direction by fitting the projection formed in the groove extending in the axial direction to the inner surface of the main body is formed projecting in the radial direction than the outer circumference of the annular pleat 휜.

As a method for producing the heat exchange gas, for example, a tapered tubular introduction member having a tapered portion is detachably attached to the main body at one end thereof so that one end thereof has substantially the same inner diameter as the main body, and the wall thickness thereof becomes thinner toward the other end thereof. It is known to attach the heat exchanger for the Stirling Refrigerator in the axial direction from the other end of the introduction member. In the heat exchange gas produced by this method, when the annular corrugation 휜 passes through the introduction member, the shape of the periphery changes, so that the contact area of the inner surface of the main body is enlarged. Therefore, the heat conduction efficiency of the annular corrugated fin can be improved, and the heat exchange gas excellent in the heat exchange performance can be provided.

In addition, the heat exchanger for a sterling refrigerator of the present invention has an annular pleat 한 formed in a cylindrical shape so that the grooves are parallel to the axial direction by the pleating process, and an outer ring member contacting the outer circumference of the annular pleat 휜. Is integrated.

If these annular corrugations 휜 and the outer ring-shaped member are integrated, these contact areas are increased and good thermal conductivity is displayed. In addition, by the integration, the heat exchanger can be easily handled and exchanged and repaired. Therefore, it is very economical and rich in recycling. Moreover, what is necessary is just to perform a bonding means, for example, brazing and brazing.

The heat exchanger gas of the present invention is obtained by inserting the heat exchanger for sterling refrigerator into the tubular body hollow. In this case, if the inner diameter of the main body is made slightly smaller than the outer diameter of the heat exchanger, the heat exchanger can be attached to the main body by pressing without welding or welding. In addition, the taper may be easily inserted into at least one end of the main body so that the wall thickness becomes thinner toward the end side along the axial direction.

In addition, the annular pleat 말 is easily rolled by connecting the end face of the inverted V-shaped groove of the other end and the end side of the V-shaped groove of the one end of the V-shaped groove in a tubular shape. Can be made.

Alternatively, the straight pleats 되는 where the V-shaped grooves are continuously connected may be rolled in a tubular shape, and the end edge of the V-shaped groove at one end and the other end of the reverse V-shaped groove at the other end may be connected to each other by spot welding on the surface. .

Alternatively, the straight pleats 되는 where the V-shaped grooves are continuously connected may be wound, and the V-shaped groove at one end thereof may be connected by soldering the end side and the end side of the reverse V-shaped groove at the other end to the surface. .

Alternatively, roll the straight pleat 되는 where the V-shaped grooves are connected continuously in a tubular shape, and hold end edges of the reverse V-shaped grooves at both ends thereof so as to contact the surface with each other. You may connect by attaching a joining member.

Alternatively, the slit is formed in one end of the inverse V-shaped groove of one end of the inverse V-shaped groove, and the slit formed on the other side from the side of the straight pleat 되는, in which the V-shaped groove is continuously connected, and the straight pleat 휜. The slits formed from one side to the other side of the straight pleat 측 may be connected to the end of the reverse V-shaped groove of the other end of the other end by sandwiching each other.

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described with reference to drawings. In addition, the same code | symbol is attached | subjected to the member of the same name as the prior art shown in FIGS. In addition, although each embodiment demonstrates only the radiator 4 and its heat exchanger 42, it is applicable also to the heat absorber 2 and the heat exchanger 22 about the structure, material selection of a member, a design change, etc. have. Therefore, of course, unless otherwise specifically mentioned, you may replace the radiator 4 and the heat exchanger 42 with the heat absorber 2 and the heat exchanger 22 in description.

A first embodiment of the present invention will be described. 1 is an external perspective view of a radiator 4 which is a heat exchanger gas of the present embodiment. 2A is an external perspective view showing the heat exchanger 42 of the radiator 4, and FIG. 2B is an exploded perspective view thereof. 3 is an enlarged plan view of a part of the radiator viewed from the axial direction.

This heat exchanger 42 consists of an annular corrugated fin 421 and an inner ring-shaped member 422. The annular corrugated fin 421 is formed by molding a corrugated thin plate into a cylindrical shape such that each groove 421a is parallel to the axial direction. The inner ring-shaped member 422 is a cylinder made of a material having good thermal conductivity.

First, the manufacturing method of the annular wrinkles 421 used by this embodiment is demonstrated. 6A to 6C show a manufacturing procedure of the annular pleat fin 421, and FIG. 6A is a plan view showing the straight pleat fin 420, and FIG. An enlarged plan view showing the form, and FIG. 6C is an enlarged plan view showing the completed annular pleat fin 421.

As shown in Fig. 6A, one end of the straight corrugated fin 420 to which the V-shaped groove 420e is continuously connected is a V-shaped groove 420a, and the other end is an inverted V-shaped groove 420b. Further, the length L1 of the end side 420c of the groove 420a and the end side 420d of the groove 420b is shorter than the length L of the inclined side between the top portions 420f of the groove 420e therebetween. It is processed.

Then, by bending in the directions of arrows F1 and F2 in Fig. 6A, the straight wrinkles 420 are rolled into a cylindrical shape, and the end edge 420c and the end edge 420d are approached as shown in Fig. 6B, and as shown in Fig. 6C, they By engaging the end edges 420c and 420d with each other, the annular wrinkled fin 421 is formed. As a result, the annular pleats 421 are pulled from each other by the edges 420c and 420d which are caught to return to the original straight form, so that the annular form of the annular pleats 421 is maintained. Reference numeral 421d is a connection portion thereof.

As shown in Figs. 2A and 5, the inner ring-shaped members 422 are concentric with each other on the inner circumference of the annular corrugated fin (421) (the axis of the annular corrugated fin (421) and the axis of the ring-shaped member (422)). I'm in contact. Here, the diameter of the circle which can smoothly connect each bottom part 421b of the annular corrugation fin 421 (the inner diameter of the annular corrugation fin 421) and the outer diameter of the inner ring-shaped member 422 are substantially the same.

These annular corrugated fins 421 and the inner ring-shaped member 422 are joined by an annular brazing material 13. That is, as shown in FIG. 2B, when the brazing material 13 is heated with the annular pleat fin 421 and the inner ring-shaped member 422 contacted with each other, the melted brazing material 13 is an annular pleat fin 421. It flows down along the bottom part 421b.

As a result, as shown in FIG. 3, the brazing material 13 reaches the portion where the annular corrugated fin 421 and the inner ring-shaped member 422 come into contact with each other almost uniformly. As the brazing material 13 is cured, the annular corrugated fin 421 and the inner ring member 422 are integrally joined together. In addition, although soldering was demonstrated here, soldering other than this may be performed.

The heat exchanger 42 mentioned above is inserted into the main body 41 shown in FIG. 1 so that shafts may be concentric with each other, and becomes 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. 4, which is a schematic cross-sectional view of the main body 41 and the heat exchanger 42, tapers are formed at both ends of the main body 41 so that the wall thickness becomes thinner toward the end side along the axial direction (taper). Part 41a).

The outer diameter of the heat exchanger 42 (the outer diameter of the annular corrugation 휜 421) R1 (= φ B) is slightly smaller than the maximum inner diameter R2 (= φ B + α ₁ ) at both end faces of the main body 41, and also tapered. It is comprised slightly larger than the internal diameter R3 (= (phi) B- (alpha) ₂ ) in an axial direction inside the part 41a.

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

Here, since each bottom portion 421b of the annular pleat fin 421 is fixed to the inner ring-shaped member 422, the annular pleat fin 421 stored in the main body 41 of the inner diameter R3 smaller than the outer diameter R1 is each The groove 421a becomes widened, and elastic force is generated in the radially outer side.

In addition, since the annular corrugation fin 421 has a constant outer diameter R1 and a depth of each groove 521a in the axial direction, the heat exchanger 42 is uniformly pressed against the inner circumferential surface of the main body 41 by the elastic force. It is fixed. At this time, the annular corrugated fin 21 and the inner ring-shaped member 422 are firmly fixed and do not deform.

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

If the annular corrugated fin 421 is damaged, the heat exchanger 42 may be taken out of the main body 41 and taken out. Therefore, the replacement can be easily carried out as necessary, so that the economic burden and recycling problems of the user at the time of repair can be eliminated.

In addition, since the heat exchanger 42 used in the present embodiment integrates the annular corrugated fin 421 and the inner ring-shaped member 422 with light solder, soft solder, or the like, the heat exchanger 42 exhibits better thermal conductivity than that of a separate structure. . Thus, the heat exchange efficiency is improved.

Next, a second embodiment of the present invention will be described. 7 is an enlarged plan view of the radiator 4 according to the present embodiment as seen from the axial direction. The heat exchanger 4 of this embodiment is equipped with the heat exchanger 42 and the heat exchanger 42 which consist of the annular corrugated fin 421 and the inner ring-shaped member 422 soldered inside like the said 1st Embodiment. It consists of a cylindrical body 41.

First, the manufacturing method of the annular wrinkles 421 used by this embodiment is demonstrated. 8A to 8C show a manufacturing procedure of the annular pleat fin 421, and FIG. 8A is a plan view showing the straight pleat fin 420, and FIG. An enlarged plan view showing a form, and FIG. 8C is an enlarged plan view showing a part of the completed annular pleat fin 421.

As shown in Fig. 8A, one end of the straight corrugated fin 420 to which the grooves 420e having a V-shaped cross section are continuously connected is a V-shaped groove 420a, and the other end is an inverted V-shaped groove 420b. In addition, the length L2 of the end side 420c of the groove 420a and the end side 420d of the groove 420b together between the top 420f and the top 420f of the groove 420e therebetween. It is processed shorter than the length L of the inclined side.

Then, by bending in the directions of arrows F1 and F2 in Fig. 8A, the straight pleat fin 420 is rolled into a cylindrical shape, and soldered or spot welded to a part of the surface of the end edge 420c and the end edge 420d approached as shown in Fig. 8B. By performing the bonding in a contact state, an annular pleat fin 421 as shown in Fig. 8C is formed. Reference numeral 421e denotes a solder or welded portion thereof.

As shown in FIGS. 2A and 7, the inner ring members 422 are in contact with each other so that the shafts are concentric with each other on the inner circumference of the annular pleat fin 421. Here, the diameter of the circle (inner diameter of the annular corrugated fin 421) which can smoothly connect each bottom part 421b of the annular corrugated fin 421 and the outer diameter of the inner ring-shaped member 422 are substantially the same.

These annular corrugated fins 421 and the inner ring-shaped member 422 are joined by an annular brazing material 13. That is, as shown in FIG. 2B, when the brazing material 13 is heated with the annular pleat fin 421 and the inner ring-shaped member 422 contacted with each other, the melted brazing material 13 is an annular pleat fin 421. It flows down along the bottom part 421b.

As a result, as shown in FIG. 3, the brazing material 13 reaches the portion where the annular corrugated fin 421 and the inner ring-shaped member 422 come into contact with each other almost uniformly. As the brazing material 13 is cured, the annular corrugated fin 421 and the inner ring member 422 are integrally joined together. In addition, although soldering was demonstrated here, soldering other than this may be performed.

The heat exchanger 42 mentioned above is inserted into the main body 41 shown in FIG. 1 so that shafts may be concentric with each other, and becomes 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. 4, which is a schematic cross-sectional view of the main body 41 and the heat exchanger 42, tapers are formed at both ends of the main body 41 so that the wall thickness becomes thinner toward the end side along the axial direction (taper). Part 41a).

The outer diameter of the heat exchanger 42 (the outer diameter of the annular corrugation 휜 421) R1 (= φ B) is slightly smaller than the maximum inner diameter R2 (= φ B + α ₁ ) at both end faces of the main body 41, and also tapered. It is comprised slightly larger than the internal diameter R3 (= (phi) B- (alpha) ₂ ) in an axial direction inside the part 41a.

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

Here, since each bottom portion 421b of the annular pleat fin 421 is fixed to the inner ring-shaped member 422, the annular pleat fin 421 stored in the main body 41 of the inner diameter R3 smaller than the outer diameter R1 is each The groove 421a becomes widened, and elastic force is generated in the radially outer side.

In addition, since the annular corrugation fin 421 has a constant outer diameter R1 and a depth of each groove 521a in the axial direction, the heat exchanger 42 is uniformly pressed against the inner circumferential surface of the main body 41 by the elastic force. It is fixed. At this time, the annular pleat fin 21 and the inner ring member 422 are firmly fixed and do not deform.

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

If the annular corrugated fin 421 is damaged, the heat exchanger 42 may be taken out of the main body 41 and taken out. Therefore, the replacement can be easily carried out as necessary, so that the economic burden and recycling problems of the user at the time of repair can be eliminated.

In addition, the heat exchanger 42 used in the present embodiment integrates the annular corrugated fin 421 and the inner ring-shaped member 422 with light solder, soft solder, or the like, and exhibits better thermal conductivity than that of a separate structure. . Thus, the heat exchange efficiency is improved.

Next, a third embodiment of the present invention will be described. 9 is a plan view of a part of the radiator 4 according to the present embodiment as seen from the axial direction. The heat exchanger 4 of this embodiment is equipped with the heat exchanger 42 and the heat exchanger 42 which consist of the annular corrugated fin 421 and the inner ring-shaped member 422 soldered inside like the said 1st Embodiment. It consists of a cylindrical body 41.

First, the manufacturing method of the annular wrinkles 421 used by this embodiment is demonstrated. 10A to 10B show a manufacturing procedure of the annular pleat fin 421, and FIG. 10A is a plan view showing the straight pleat fin 420, and FIG. An enlarged plan view showing a form, and FIG. 10C is an enlarged plan view showing a part of the completed annular pleat fin 421.

As shown in Fig. 10A, one end of the straight corrugated fin 420 to which the grooves 420e having a V-shaped cross section are continuously connected is a V-shaped groove 420a, and the other end is an inverted V-shaped groove 420b. Further, the length L3 of the end side 420c of the groove 420a and the end side 420d of the groove 420b together is between the top 420f and the top 420f of the groove 420e therebetween. It is processed shorter than the length L of the inclined side.

Then, bent in the directions of arrows F1 and F2 in Fig. 10A, and the straight wrinkles 420 are rolled in a cylindrical shape so as to align end edges 420c and 420d previously coated with an adhesive 16 such as an instant adhesive on the surface (Fig. 10B). In addition, the end face 420c and the application surface of the adhesive 16 on the end side 420d are brought into contact with each other for a while to be held, thereby adhering and forming an annular pleat fin 421 as shown in Fig. 10C. Reference numeral 421f denotes an adhesive portion.

As shown in Figs. 2A and 9, the inner ring-shaped members 422 are in contact with each other so that the shafts are concentric with each other on the inner circumference of the annular corrugated fin 421. Here, the diameter of the circle (inner diameter of the annular corrugated fin 421) which can smoothly connect each bottom part 421b of the annular corrugated fin 421 and the outer diameter of the inner ring-shaped member 422 are substantially the same.

These annular corrugated fins 421 and the inner ring-shaped member 422 are joined by an annular brazing material 13. That is, as shown in FIG. 2B, when the brazing material 13 is heated with the annular pleat fin 421 and the inner ring-shaped member 422 contacted with each other, the melted brazing material 13 is an annular pleat fin 421. It flows down along the bottom part 421b.

As a result, as shown in FIG. 3, the brazing material 13 reaches the portion where the annular corrugated fin 421 and the inner ring-shaped member 422 come into contact with each other almost uniformly. As the brazing material 13 is cured, the annular corrugated fin 421 and the inner ring member 422 are integrally joined together. In addition, although soldering was demonstrated here, soldering other than this may be performed.

The heat exchanger 42 mentioned above is inserted into the main body 41 shown in FIG. 1 so that shafts may be concentric with each other, and becomes 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. 4, which is a schematic cross-sectional view of the main body 41 and the heat exchanger 42, tapers are formed at both ends of the main body 41 so that the wall thickness becomes thinner toward the end side along the axial direction (taper). Part 41a).

The outer diameter of the heat exchanger 42 (the outer diameter of the annular corrugation 휜 421) R1 (= φ B) is slightly smaller than the maximum inner diameter R2 (= φ B + α ₁ ) at both end faces of the main body 41, and also tapered. It is comprised slightly larger than the internal diameter R3 (= (phi) B- (alpha) ₂ ) in an axial direction inside the part 41a.

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

Here, since each bottom portion 421b of the annular pleat fin 421 is fixed to the inner ring-shaped member 422, the annular pleat fin 421 stored in the main body 41 of the inner diameter R3 smaller than the outer diameter R1 is each The groove 421a becomes widened, and elastic force is generated in the radially outer side.

In addition, since the annular corrugation fin 421 has a constant outer diameter R1 and a depth of each groove 521a in the axial direction, the heat exchanger 42 is uniformly pressed against the inner circumferential surface of the main body 41 by the elastic force. It is fixed. At this time, the annular pleat fin 21 and the inner ring member 422 are firmly fixed and do not deform.

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

If the annular corrugated fin 421 is damaged, the heat exchanger 42 may be taken out of the main body 41 and taken out. Therefore, the replacement can be easily carried out as necessary, so that the economic burden and recycling problems of the user at the time of repair can be eliminated.

In addition, the heat exchanger 42 used in the present embodiment integrates the annular corrugated fin 421 and the inner ring-shaped member 422 with light solder, soft solder, or the like, and exhibits better thermal conductivity than that of a separate structure. . Thus, the heat exchange efficiency is improved.

Next, a fourth embodiment of the present invention will be described. 11 is a plan view of a part of the radiator 4 according to the present embodiment as seen from the axial direction. The heat exchanger 4 of this embodiment is equipped with the heat exchanger 42 and the heat exchanger 42 which consist of the annular corrugated fin 421 and the inner ring-shaped member 422 soldered inside like the said 1st Embodiment. It consists of a cylindrical body 41.

First, the manufacturing method of the annular wrinkles 421 used by this embodiment is demonstrated. 12A to 12C show a manufacturing procedure of the annular pleat fin 421, and FIG. 12A is a plan view showing the straight pleat fin 420, and FIG. 12B is a roll of the straight pleat fin 420 to approach both ends. An enlarged plan view showing a form, and FIG. 12C is an enlarged plan view showing a part of the completed annular pleat fin 421.

As shown in Fig. 12A, one end of the straight corrugated fin 420 in which the grooves 420e having a V-shaped cross section are continuously connected is a V-shaped groove 420a, and the other end is an inverted V-shaped groove 420b. In addition, the length L4 of the end side 420c of the groove 420a and the end side 420d of the groove 420b is between the top 420f and the top 420f of the groove 420e therebetween. It is processed shorter than the length L of the inclined side.

Then, bent in the directions of arrows F1 and F2 in Fig. 12A, and the corrugated fin 420 is rolled so as to fit end edges 420c and 420d previously uniformly coated with paste-like solder 17 on the surface (Fig. 12B). Then, the end side 420c and the application surface of the solder 17 on the end side 420d are brought into contact with each other to be heated and soldered for a while to form an annular pleat fin 421 as shown in Fig. 12C. Reference numeral 421g is a solder or welded portion thereof.

As shown in Figs. 2A and 11, the inner ring-shaped members 422 are in contact with each other so that their axes are concentric with each other on the inner circumference of the annular corrugated fin 421. Here, the diameter of the circle (inner diameter of the annular corrugated fin 421) which can smoothly connect each bottom part 421b of the annular corrugated fin 421 and the outer diameter of the inner ring-shaped member 422 are substantially the same.

These annular corrugated fins 421 and the inner ring-shaped member 422 are joined by an annular brazing material 13. That is, as shown in FIG. 2B, when the brazing material 13 is heated with the annular pleat fin 421 and the inner ring-shaped member 422 contacted with each other, the melted brazing material 13 is an annular pleat fin 421. It flows down along the bottom part 421b.

As a result, as shown in FIG. 3, the brazing material 13 reaches the portion where the annular corrugated fin 421 and the inner ring-shaped member 422 come into contact with each other almost uniformly. As the brazing material 13 is cured, the annular corrugated fin 421 and the inner ring member 422 are integrally joined together. In addition, although soldering was demonstrated here, soldering other than this may be performed.

The heat exchanger 42 mentioned above is inserted into the main body 41 shown in FIG. 1 so that shafts may be concentric with each other, and becomes 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. 4, which is a schematic cross-sectional view of the main body 41 and the heat exchanger 42, tapers are formed at both ends of the main body 41 so that the wall thickness becomes thinner toward the end side along the axial direction (taper). Part 41a).

The outer diameter of the heat exchanger 42 (the outer diameter of the annular corrugation 휜 421) R1 (= φ B) is slightly smaller than the maximum inner diameter R2 (= φ B + α ₁ ) at both end faces of the main body 41, and also tapered. It is comprised slightly larger than the internal diameter R3 (= (phi) B- (alpha) ₂ ) in an axial direction inside the part 41a.

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

Here, since each bottom portion 421b of the annular pleat fin 421 is fixed to the inner ring-shaped member 422, the annular pleat fin 421 stored in the main body 41 of the inner diameter R3 smaller than the outer diameter R1 is each The groove 421a becomes widened, and elastic force is generated in the radially outer side.

In addition, since the annular corrugation fin 421 has a constant outer diameter R1 and a depth of each groove 521a in the axial direction, the heat exchanger 42 is uniformly pressed against the inner circumferential surface of the main body 41 by the elastic force. It is fixed. At this time, the annular pleat fin 21 and the inner ring member 422 are firmly fixed and do not deform.

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

If the annular corrugated fin 421 is damaged, the heat exchanger 42 may be taken out of the main body 41 and taken out. Therefore, the replacement can be easily carried out as necessary, so that the economic burden and recycling problems of the user at the time of repair can be eliminated.

In addition, the heat exchanger 42 used in the present embodiment integrates the annular corrugated fin 421 and the inner ring-shaped member 422 with light solder, soft solder, or the like, and exhibits better thermal conductivity than that of a separate structure. . Thus, the heat exchange efficiency is improved.

Next, a fifth embodiment of the present invention will be described. 13 is a plan view of a part of the radiator 4 according to the present embodiment as seen from the axial direction. The heat exchanger 4 of this embodiment is equipped with the heat exchanger 42 and the heat exchanger 42 which consist of the annular corrugated fin 421 and the inner ring-shaped member 422 soldered inside like the said 1st Embodiment. It consists of a cylindrical body 41.

First, the manufacturing method of the annular wrinkles 421 used by this embodiment is demonstrated. 14A to 14C show a manufacturing procedure of the annular pleat fin 421, and FIG. 14A is a plan view showing the straight pleat fin 420, and FIG. 14B is a roll of the straight pleat fin 420, approaching both ends thereof. An enlarged plan view showing a form, and FIG. 14C is an enlarged plan view showing a part of the completed annular pleat fin 421.

As shown in Fig. 14A, one end of the straight corrugated fin 420 to which the grooves 420e having a V-shaped cross section are continuously connected is a V-shaped groove 420a, and the other end is an inverted V-shaped groove 420b. In addition, the length L5 of the end side 420c of the groove 420a and the end side 420d of the groove 420b together is between the top 420f and the top 420f of the groove 420e therebetween. It is processed shorter than the length L of the inclined side.

Then, by bending in the directions of arrows F1 and F2 in Fig. 14A, the end edges 420c and 420d are rolled with a straight pleat fin 420 (Fig. 14B), and the end edges 420c and the end edges 420d are surfaced to each other. It is held in contact with the front surface thereof and is connected by a cross-sectional U-shaped joining member 18 made of a material having a strong elasticity, thereby forming an annular corrugation pin 421 as shown in Fig. 14C.

As shown in Figs. 2A and 13, the inner ring members 422 are in contact with each other so that their axes are concentric with each other on the inner circumference of the annular pleat fin 421. Here, the diameter of the circle (inner diameter of the annular corrugated fin 421) which can smoothly connect each bottom part 421b of the annular corrugated fin 421 and the outer diameter of the inner ring-shaped member 422 are substantially the same.

These annular corrugated fins 421 and the inner ring-shaped member 422 are joined by an annular brazing material 13. That is, as shown in Fig. 2B, when the brazing material 13 is heated with the annular pleat fin 421 and the inner ring-shaped member 422 in contact with each other, the molten solder material 13 is an annular pleat fin 421. It flows down along the bottom part 421b.

As a result, as shown in FIG. 3, the brazing material 13 reaches the portion where the annular corrugated fin 421 and the inner ring-shaped member 422 come into contact with each other almost uniformly. As the brazing material 13 is cured, the annular corrugated fin 421 and the inner ring member 422 are integrally joined together. In addition, although soldering was demonstrated here, soldering other than this may be performed.

The heat exchanger 42 mentioned above is inserted into the main body 41 shown in FIG. 1 so that shafts may be concentric with each other, and becomes 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. 4, which is a schematic cross-sectional view of the main body 41 and the heat exchanger 42, tapers are formed at both ends of the main body 41 so that the wall thickness becomes thinner toward the end side along the axial direction (taper). Part 41a).

The outer diameter of the heat exchanger 42 (the outer diameter of the annular corrugation 휜 421) R1 (= φ B) is slightly smaller than the maximum inner diameter R2 (= φ B + α ₁ ) at both end faces of the main body 41, and also tapered. It is comprised slightly larger than the internal diameter R3 (= (phi) B- (alpha) ₂ ) in an axial direction inside the part 41a.

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

Here, since each bottom portion 421b of the annular pleat fin 421 is fixed to the inner ring-shaped member 422, the annular pleat fin 421 stored in the main body 41 of the inner diameter R3 smaller than the outer diameter R1 is each The groove 421a becomes widened, and elastic force is generated in the radially outer side.

In addition, since the annular corrugation fin 421 has a constant outer diameter R1 and a depth of each groove 521a in the axial direction, the heat exchanger 42 is uniformly pressed against the inner circumferential surface of the main body 41 by the elastic force. It is fixed. At this time, the annular pleat fin 21 and the inner ring member 422 are firmly fixed and do not deform.

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

If the annular corrugated fin 421 is damaged, the heat exchanger 42 may be taken out of the main body 41 and taken out. Therefore, the replacement can be easily carried out as necessary, so that the economic burden and recycling problems of the user at the time of repair can be eliminated.

In addition, the heat exchanger 42 used in the present embodiment integrates the annular corrugated fin 421 and the inner ring-shaped member 422 with light solder, soft solder, or the like, and exhibits better thermal conductivity than that of a separate structure. . Thus, 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 as seen from the axial direction. The heat exchanger 4 of this embodiment is equipped with the heat exchanger 42 and the heat exchanger 42 which consist of the annular corrugated fin 421 and the inner ring-shaped member 422 soldered inside like the said 1st Embodiment. It consists of a cylindrical body 41.

First, the manufacturing method of the annular wrinkles 421 used by this embodiment is demonstrated. Fig. 16 shows a manufacturing procedure of the annular pleat pin 421, and Fig. 16a is a plan view showing the straight pleat pin 420, and Fig. 16b shows the form in which both ends are rolled up to approach the both ends. 16C is an enlarged plan view showing the completed annular pleat fin 421, and FIG. 17 is a perspective view of the main part of FIG. 16B.

As shown in Fig. 16A, one end of the straight corrugated fin 420 to which the grooves 420e having a V-shaped cross section are continuously connected is a V-shaped groove 420a, and the other end is an inverted V-shaped groove 420b. In addition, the length L6 of the end side 420c of the groove 420a and the end side 420d of the groove 420b together is between the top 420f and the top 420f of the groove 420e therebetween. It is processed shorter than the length L of the inclined side. In addition, as shown in Fig. 17, end edges 420c and 420d are provided with slits 19 extending toward one side surface 420g of straight corrugated fin 420. As shown in Figs.

Then, by bending in the directions of arrows F1 and F2 in Fig. 16A, the straight wrinkles 420 are rolled in a cylindrical shape so as to align the end edges 420c and 420d (Fig. 16B), and the slit 19 of the end edge 420c. By connecting the end edges 420c and 420d so that the slit 19 and the slit 19 of the end edge 420d are alternately fitted, an annular pleat fin 421 as shown in Fig. 16C is formed.

As shown in Figs. 2A and 15, the inner ring-shaped members 422 are in contact with each other so that their axes are concentric with each other on the inner circumference of the annular pleat fin 421. Here, the diameter of the circle (inner diameter of the annular corrugated fin 421) which can smoothly connect each bottom part 421b of the annular corrugated fin 421 and the outer diameter of the inner ring-shaped member 422 are substantially the same.

These annular corrugated fins 421 and the inner ring-shaped member 422 are joined by an annular brazing material 13. That is, as shown in FIG. 2B, when the brazing material 13 is heated with the annular pleat fin 421 and the inner ring-shaped member 422 contacted with each other, the melted brazing material 13 is an annular pleat fin 421. It flows down along the bottom part 421b.

As a result, as shown in FIG. 3, the brazing material 13 reaches the portion where the annular corrugated fin 421 and the inner ring-shaped member 422 come into contact with each other almost uniformly. As the brazing material 13 is cured, the annular corrugated fin 421 and the inner ring member 422 are integrally joined together. In addition, although soldering was demonstrated here, soldering other than this may be performed.

The heat exchanger 42 mentioned above is inserted into the main body 41 shown in FIG. 1 so that shafts may be concentric with each other, and becomes 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. 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 side along the axial direction (taper). Part 41a).

The outer diameter of the heat exchanger 42 (the outer diameter of the annular corrugation 휜 421) R1 (= φ B) is slightly smaller than the maximum inner diameter R2 (= φ B + α ₁ ) at both end faces of the main body 41, and also tapered. It is comprised slightly larger than the internal diameter R3 (= (phi) B- (alpha) ₂ ) in an axial direction inside the part 41a.

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

Here, since each bottom portion 421b of the annular pleat fin 421 is fixed to the inner ring-shaped member 422, the annular pleat fin 421 stored in the main body 41 of the inner diameter R3 smaller than the outer diameter R1 is each The groove 421a becomes widened, and elastic force is generated in the radially outer side.

In addition, since the annular corrugation fin 421 has a constant outer diameter R1 and a depth of each groove 521a in the axial direction, the heat exchanger 42 is uniformly pressed against the inner circumferential surface of the main body 41 by the elastic force. It is fixed. At this time, the annular pleat fin 21 and the inner ring member 422 are firmly fixed and do not deform.

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

If the annular corrugated fin 421 is damaged, the heat exchanger 42 may be taken out of the main body 41 and taken out. Therefore, the replacement can be easily carried out as necessary, so that the economic burden and recycling problems of the user at the time of repair can be eliminated.

In addition, the heat exchanger 42 used in the present embodiment integrates the annular corrugated fin 421 and the inner ring-shaped member 422 with light solder, soft solder, or the like, and exhibits better thermal conductivity than that of a separate structure. . Thus, the heat exchange efficiency is improved.

A seventh embodiment of the present invention will be described. 18 is a plan view of the radiator 4 according to the present embodiment as seen from the axial direction. The heat exchanger 4 of this embodiment is equipped with the heat exchanger 42 and the heat exchanger 42 which consist of the annular corrugated fin 421 and the inner ring-shaped member 422 soldered inside like the said 1st Embodiment. It consists of a cylindrical body 41.

First, the manufacturing method of the annular wrinkles 421 used by this embodiment is demonstrated. 19A to 19C show the manufacturing procedure of the annular corrugated fin 421, and FIG. 19A is a plan view showing the linear corrugated fin 420, and FIG. 19B is rolled up the linear corrugated fin 420 to approach both ends thereof. It is a top view which shows the formed annular wrinkles 421, and FIG. 19C is a top view of the cylindrical main body 41. FIG.

As shown in Fig. 19A, one end and the other end of the straight pleat fin 420 to which the grooves 420e having a V-shaped cross section are continuously connected are inverted V-shaped grooves 420b. In addition, the length L7 of the end side 420c and the end side 420d of the groove 420b at both ends is the length of the inclined side between the top 420f and the top 420f of the groove 420e therebetween. It is processed longer than L.

Then, bent in the directions of arrows F1 and F2 in Fig. 19A, and the straight wrinkles 420 are not cylindrical, so as to align the end edges 420c and 420d (Fig. 16B), at least the end edge 420c and the end face 420d. By holding in the form in which the tip portions of the in contact with each other, an annular pleat fin 421 as shown in Fig. 19B is formed. As a result, the tip portions of the end edges 420c and 420d protrude radially outwardly from the outer circumference of the annular corrugated fin 421 (the circumference of the circle that can smoothly connect the top portions 421c). To form.

The inner diameter of the cylindrical body 41 is selected to be substantially the same as the outer diameter of the annular corrugated fin 421. Moreover, as shown to FIG. 19C, the recess 41a which can be fitted with the protrusion part 421h of the annular corrugation fin 421 is extended in the axial direction in one part of the inner surface of the outer heat exchanger 3.

The annular pleat fin 421 aligns its center with the central axis of the main body 41, and inserts the protrusion 421h into the recess 41a of the main body to insert it in the axial direction. At this time, as shown in Fig. 1, one end surface of the annular corrugated fin 421 is inserted to a position coinciding with the open end of the main body 41.

A force to return to the original straight pleat 휜 420 acts on the protrusion 421h of the annular pleat 421, but the protruding portion 421h is in a state where the movement is restricted in the recess 41a. 421 changes with the force to spread in the radial direction. Therefore, the annular corrugated fin 421 is spread and pressed to the inner surface of the main body 41, so that it can be held and held in a predetermined position while maintaining its shape.

On the other hand, the outer diameter of the cylindrical inner ring-shaped member 422 is selected to be substantially the same as the inner diameter of the annular corrugated fin 421 (the diameter of the circle which can smoothly connect the groove 2b). The center of the inner ring-shaped member 422 is inserted in the axial direction in accordance with the central axis of the annular corrugated fin 421 in the main body 1. Then, the heat exchanger 42 is mounted in the main body 41 by soldering and integrating the inner peripheral portion of the annular corrugated fin 421 and the contact portion of the outer surface of the inner ring-shaped member 422, so that the radiator 4 as shown in FIG. Obtained.

Therefore, the process of adhering and welding the annular corrugated fin 421 to the main body 41 can be omitted, and the productivity can be improved, and the annular corrugated fin 421 can be reliably fixed by pressing. Since it is possible to obtain a uniform contact form across the entire circumference of the annular corrugated fin 421, it is possible to stably provide the radiator 4 having excellent performance.

Next, an eighth embodiment according to the present invention will be described. 20 is an external perspective view of a radiator 4 which is a heat exchange gas of the present embodiment. 21A is an external perspective view showing the heat exchanger 42 'incorporated in the radiator 4, and FIG. 21B is an exploded perspective view thereof.

This heat exchanger 42 'consists of an annular corrugated fin 421 and an outer ring-shaped member 422'. The annular corrugated fin 421 is produced by the procedure described in each of the first to seventh embodiments. The outer ring member 422 'is a cylinder made of a material having good thermal conductivity and elasticity.

As shown in Fig. 21A, the outer ring-shaped members 422 'are in contact with each other on the outer circumference of the annular pleat fin 421 so as to be concentric with each other. Here, the outer diameter of the annular corrugated fin 421 and the inner diameter of the outer ring-shaped member 422 'are almost the same. As shown in Fig. 22, the annular corrugated fin 421 and the outer ring member 422 'have a brazing material 13 similar to the annular corrugated fin 421 and the inner annular member 422 of the first embodiment. It is bonded and fixed with solder or the like.

The heat exchanger 42 'mentioned above is inserted into the main body 41 shown in FIG. 20 so that shafts may be concentric with each other, and becomes 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 ', tapered portions are formed at both ends of the main body 41 as in the first embodiment (taper portion 41a). .

The outer diameter of the heat exchanger 42 '(the outer diameter of the outer ring-shaped member 422') R1 '(=? B') is the maximum inner diameter R2 '(=? B' +? ₁ 'at both end faces of the main body 41). It is a little smaller than), and is slightly larger than the inner diameter R3 '(= phi B'-(alpha) ₂ ') in an axial direction inside the taper part 41a.

Therefore, like the said 1st Embodiment, the heat exchanger 42 'can be inserted in the main body 41 simply by the taper part 41a. Moreover, the heat exchanger 42 'accommodated in the main body 41 is pressed against the inner circumferential surface of the main body 41 and fixed by the elastic force generated in the annular corrugated fin 421 and the outer ring-shaped member 422'. At this time, the annular corrugation fin 421 and the outer ring member 422 'are firmly fixed and do not deform.

As described above, the present embodiment can also fix the heat exchanger 42 'at an appropriate position in the main body 41 without using an adhesive or solder, and the main body 41 and the heat exchanger 42' are fixed. Because it does not, it can be taken out as possible. In addition, the annular corrugated fin 421 and the outer ring member 422 'are integrated to exhibit even better thermal conductivity.

A ninth embodiment of the present invention will be described with reference to the drawings. 24 is an enlarged plan view of a part of the radiator 4 according to the present embodiment as seen from the axial direction. FIG. 25 is a part of the manufacturing procedure of the radiator 4, FIG. 25A is a sectional view before inserting the heat exchanger 42 on the introduction member 14 side, and FIG. 25B is a sectional view after its insertion.

As shown in Figs. 25A and 25B, the cylindrical 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 the same as that of the main body 411, and the inner diameter thereof is substantially the same as the inner diameter of the main body 41 at the joining portion, and the taper portion increases as it is separated from the joining portion ( It is a cross-sectional shape of the inner surface which has 14a).

Hereinafter, the manufacturing procedure of the radiator 4 which concerns on this embodiment is demonstrated with reference to FIG. 25A and 25B. As described in the first to sixth embodiments, the annular corrugated fin 421 is rolled up to form an annular shape by rolling the straight corrugated fin 420 and fixing both ends thereof. In addition, the annular corrugated fin 421 is formed of a material rich in flexibility that is easily deformed by an external force.

In the annular corrugated fin 421, the inner ring member 422 selected by the outer diameter slightly larger than the inner diameter is inserted from the axial direction, and the heat exchanger 42 is produced. 25A, the heat exchanger 42 is inserted in the axial direction from the open end of the introduction member 14. As shown in FIG. As a result, the annular corrugated fin 421 is gradually press-fitted from the place where the inner diameter is large to the small place along the tapered portion 14a of the introduction member 14 while being radially pressed from the center to the outside by the inner ring-shaped member 422. It becomes.

Then, as shown in Fig. 25B, the insertion is terminated in a state where one end surface of the annular corrugation pin 421 reaches the junction between the main body 41 and the introduction member 14. As a result, the top portion 421c of the annular corrugation fin 421 is rubbed with the inner surface of the introduction member 14, and the shape thereof deforms from an arc shape to a planar shape. The degree of this deformation becomes larger as the hardness of the material of the introduction member 14 is harder than that of the annular pleat fin 421. As a result, the contact area between the annular corrugated fin 421 and the inner surface of the main body 41 is enlarged as shown in FIG. Therefore, the efficiency of heat transfer from the annular corrugated fin 421 to the main body 41 is improved, and the improvement of the heat exchange performance of the radiator 4 is achieved.

A tenth embodiment of the present invention will be described with reference to the drawings. FIG. 26 is a plan view of the heat sink 42 according to the present embodiment, FIG. 27 is a plan view of the heat exchanger 42, and FIG. 28 is a plan view of the cylindrical body 41.

On the outer circumference of the annular pleat fin 421 ', rounded convex portions 421k are formed, and convex portions 421k adjacent to each other are in close contact with each other and lined up at equal intervals as a whole. On the other hand, the main body 41 is formed by injecting molten metal into a mold and hardening it. As shown in Fig. 28, the concave portions 41m extending in the axial direction are uniformly spaced all around the inner circumference. Is carried out. This recessed part 41m is a shape which the convex part 421k of the said annular corrugation fin 421 'can fit.

As shown in Fig. 2A, by inserting a cylindrical inner ring-shaped member 422 having an outer diameter approximately the same as its inner diameter in advance inside the corrugated fin 421 ', and soldering the contact portion, a row as shown in Fig. 27 is obtained. The exchanger 42 is produced. 4, the center of this heat exchanger 42 is inserted in the axial direction in accordance with the central axis of the main body 41. As shown in FIG. At this time, as shown in Fig. 26, since the convex portion 421k of the annular pleat fin 421 'and the concave portion 41m of the main body 41 are matched with each other, the inside of the main body 41 of the heat exchanger 42 The radiator 4 with which position fixing along the circumferential direction is sure is obtained. Therefore, according to the present embodiment, the annular corrugated fin 421 'is firmly adhered to the inner surface of the main body 41, and the contact area is secured to the entire circumference of the annular corrugated fin 421', thereby ensuring excellent performance. The radiator 4 can be provided stably.

As described above, since the heat exchanger of the present invention does not require manual adhesion with the main body, the heat exchanger can be more easily formed and the manufacturing cost can be reduced. In addition, the obtained heat exchanger gas has little variation in quality and has stable heat exchange performance.

In addition, the heat exchanger has a good thermal conductivity by integrating the corrugated fin and the inner or outer ring-shaped member, and the heat exchange efficiency is improved.

In addition, since the heat exchanger is fixed to the main body of the heat exchanger by position, the heat exchanger can be taken out of the main body and taken out. Therefore, even if wrinkles are damaged and the quality of the heat exchanger is degraded, the wrinkles can be easily exchanged as necessary, so it is very economical and suitable for recycling.

In particular, if the taper is formed at the end of the main body of the heat exchanger gas, even if the outer diameter of the heat exchanger is larger than the inner diameter of the main body, it can be inserted smoothly.

Moreover, it is not necessary to manually attach the annular pleat 내에 into the cylindrical main body by gluing or welding, and it can be reliably crimped and fixed by simple insertion. Therefore, the improvement of the productivity of a heat effect gas is achieved. In addition, it is possible to stably supply a heat exchange gas having excellent performance since it is possible to obtain a uniform contact state across the entire circumference of the annular corrugated fin.

Claims (15)

Sterling freezing, characterized in that the annular pleat 휜 formed into a cylindrical shape such that the grooves are formed in parallel with the axial direction by the pleating process, and an inner ring-shaped member in contact with the inner circumference of the annular pleat 일체 is integrated. Heat exchanger. In the heat exchanger gas formed by inserting the heat exchanger for sterling refrigerators of Claim 1 into the hollow of a tubular main body, And an inner diameter of the main body is slightly smaller than an outer diameter of the heat exchanger. The heat exchanger according to claim 2, wherein at least one end of the main body has a taper formed so that the wall thickness becomes thinner toward the end side along the axial direction, and the maximum inner diameter of the main body is larger than the outer diameter of the heat exchanger. Exchange gas. 3. The wave-shaped concave according to claim 2, wherein the convex portions of the wave form are formed in close contact with each other around the annular corrugations, and are arranged at equal intervals as a whole. And a convex portion fitted to the portion. 3. The annular pleat 휜 is formed so that the end edges of the inverted V-shaped grooves at both ends are rounded in the shape of a straight pleat 어진 whose length is longer than that of the inclined sides of the V-shaped grooves therebetween, and the edges are brought into contact with each other. It is held so that the annular pleat 휜 is produced, and is formed at the distal end of the both ends so as to fit into the groove extending in the axial direction to the inner surface of the main body a projection projecting in a radial direction from the outer circumference of the annular pleat 휜. Heat exchange gas, characterized in that one. In the method for producing a heat exchange gas according to claim 2, A tapered tubular introduction member is detachably mounted to the main body at one end thereof so that one end thereof has substantially the same inner diameter as the main body, and the wall thickness becomes thinner toward the other end thereof, and the heat exchanger for the sterling refrigerator is introduced. A method of producing a heat exchange gas, characterized in that the insertion in the axial direction from the other end of the member. Sterling freezing, characterized in that the annular pleat 한 formed in a cylindrical shape such that the grooves are formed parallel to the axial direction by the pleating process, and an outer ring-shaped member in contact with the outer circumference of the annular pleat 일체 is integrated. Heat exchanger. In the heat exchanger gas formed by inserting the heat exchanger for a sterling refrigerator according to claim 7 into a tubular body hollow, And an inner diameter of the main body is slightly smaller than an outer diameter of the heat exchanger. 10. The heat generating apparatus according to claim 8, wherein at least one end of the main body has a taper formed so that the wall thickness becomes thinner toward the end side along the axial direction, and the maximum inner diameter of the main body is larger than the outer diameter of the heat exchanger. Exchange gas. 8. The end of the annular pleat 휜 is a cylindrical pleat 되는 where the V-shaped grooves are continuously connected to each other, and ends of an end side of the V-shaped groove at one end thereof and an inverted V-shaped groove at the other end thereof. Heat exchanger for sterling refrigerator, characterized in that the connection is made by engaging the side. 8. The end of the annular pleat 휜 is a cylindrical pleat 되는 where the V-shaped grooves are continuously connected to each other, and ends of an end side of the V-shaped groove at one end thereof and an inverted V-shaped groove at the other end thereof. A heat exchanger for sterling refrigeration, characterized in that the surface is connected by performing spot welding on the surface of each other. 8. The end face of claim 1 or 7, wherein the annular pleat 말 is a cylindrical pleat with a straight pleat 되는, in which the V-shaped grooves are continuously connected, and which has an end side of the V-shaped groove at one end thereof and an inverted V-shaped groove at the other end thereof. Heat exchanger for a sterling refrigerator, characterized in that the connection is made by bonding the surfaces to each other. 8. The end of the annular pleat 휜 is a cylindrical pleat 되는 where the V-shaped grooves are continuously connected to each other, and ends of an end side of the V-shaped groove at one end thereof and an inverted V-shaped groove at the other end thereof. A heat exchanger for a sterling refrigerator, characterized in that the side surfaces are connected by soldering to each other. 8. The annular pleat (6) according to claim 1 or 7, wherein the annular pleat (6) has a cylindrical shape with a straight pleat (6) in which the V-shaped grooves are continuously connected, and retains end edges of the inverted V-shaped grooves at both ends thereof in contact with the surface. A support and heat exchanger for a sterling refrigerator, characterized in that it is connected by attaching a cross-section C-shaped joining member to a distal end of the contact portion. 8. The annular pleat (6) according to claim 1 or 7, wherein the annular pleat (6) is formed in a cylindrical shape, with a straight pleat (6) connected to the V-shaped grooves continuously connected, and from one side of the straight pleat (6) to an end side of the reverse V-shaped groove at one end thereof. And a slit formed on the other side, and a slit formed on one side from the other side of the linear pleat 에 to the end side of the inverted V-shaped groove of the other end of the straight pleat 휜 by interposing. Heat exchanger for sterling refrigerators.