JP3591707B2 - Heat exchanger for Stirling engine - Google Patents

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a heat exchanger used for a Stirling engine.
[0002]
[Prior art]
FIG. 6 (a) is a perspective view around a conventional heat exchanger for a Stirling engine, and FIGS. 6 (b) and 6 (c) are enlarged views of main parts thereof. As shown in FIG. 6 (a), the high-temperature side heat exchanger 1a and the low-temperature side heat exchanger 1b are corrugated fins inserted into the hollow portions of the cylindrical radiator 4 and the heat absorber 5 which are opened up and down, respectively. 2 is formed.
[0003]
Hereinafter, the manufacturing procedure of the high temperature side heat exchanger 1a will be described as an example. Reference numeral 2 denotes a corrugated fin, and the entire periphery of the side face is corrugated. That is, as shown in FIGS. 6B and 6C, on the side surface of the corrugated fin 2, a number of V-shaped protrusions 2a, 2a, 2a extending linearly at equal intervals along the axial direction. . And a plurality of grooves 2b, 2b, 2b,... Which are located between the protrusions 2a and 2a and have substantially the same shape as the protrusion 2a. The outer diameter of the corrugated fin 2 (the diameter of a circle formed by smoothly connecting the protruding portions 2a, 2a, 2a,...) Is selected to be substantially equal to the inner diameter of the radiator 4. Therefore, the corrugated fins 2 can be inserted into the hollow portion of the radiator 4 with their axes aligned concentrically.
[0004]
However, since the corrugated fins 2 are not fixed to the radiator 4 simply by being inserted, the corrugated fins 2 cannot be used as the heat exchanger 1a as they are. Therefore, conventionally, the projection 2a of the corrugated fin 2 and the inner peripheral surface of the radiator 4 are firmly fixed to each other by bonding or welding. In the case of bonding, as shown in FIG. 6 (b), the adhesive 14 is spread thinly on the inner peripheral surface of the radiator 4, and after inserting the corrugated fin 2 there, the corrugated fin 2 is placed at a predetermined position. It was fixed by holding for a while and drying. On the other hand, in the case of welding, first, the corrugated fin 2 is inserted into the radiator 4. Then, as shown in FIG. 6 (c), the fixing is ensured by applying welding to the portions of the inner peripheral surface of the radiator 4 and the protruding portions 2a of the corrugated fins 2 which are in contact with or close to each other. Reference numeral 15 denotes the welded portion.
[0005]
FIG. 7 is a schematic side sectional view of a free piston type Stirling refrigerator equipped with a radiator 4 and a heat absorber 5 to which the corrugated fins 2 (in this case, the heat exchangers 1a and 1b) are fixed as described above. FIG. As shown in FIG. 7, the Stirling refrigerator 20 is configured such that a displacer 7 and a piston 8 are disposed in a cylinder 6 having a cylindrical space therein, thereby forming a compression space formed in the space. A regenerator 11 is provided between the fuel cell 9 and the expansion space 10 to form a closed circuit. The working space of the closed circuit is filled with a working gas such as helium, and the piston 8 is connected to a linear motor (not shown) or the like. Is vibrated in the axial direction of the cylinder 6 by the external power. The vibration of the piston 8 causes a periodic pressure change in the working gas sealed in the compression space 9, and the working gas is supplied through the regenerator 11 to the expansion space 10 by the pulsation of the back pressure which rises with the compression. Into the tank. At this time, the displacement of the gas causes a periodic axial vibration force to be generated in the displacer 7.
[0006]
As a result, the displacer 7 has one end fixed to the displacer 7 and has the same cycle as the piston 8 by the spring 13 connected between the other end of the displacer rod 12 penetrating the piston 8 and the bottom of the cylinder 6. The cylinder 6 reciprocates in the axial direction while maintaining a predetermined phase difference. When the displacer 7 and the piston 8 reciprocate while maintaining an appropriate phase difference, the working gas sealed in the working space forms a thermodynamic cycle known as a reverse Stirling cycle, and mainly generates cold heat in the expansion space 10. .
[0007]
The principle will be described below. When the working gas in the compression space 9 compressed by the piston 8 moves to the expansion space 10 via the regenerator 11, the regenerator 11 receives the cold heat stored half a cycle before and is precooled. At this time, heat generated in the compression space 9 is released from the radiator 4 to the outside via the high-temperature side heat exchanger 1a. When most of the working gas flows into the expansion space 10, the expansion starts by pushing down the displacer 7 due to the increase in the pressure inside the space 10. Then, when the piston 13 expands to some extent, the displacer 7 is pushed up by the return force of the piston 13, and the working gas in the expansion space 10 with the increased pressure passes through the regenerator 11 and moves to the compression space 9 again. At this time, heat is taken from the outside by the heat absorber 5 via the low-temperature side heat exchanger 1b to cool the outside air. Then, when most of the working gas returns to the compression space 10, the piston 8 is compressed again and the next cycle is started. By repeating the above-described series of cycles continuously, it is possible to extract extremely low-temperature cold from the Stirling refrigerator 20.
[0008]
As described above, in the Stirling refrigerator 20 in which the working gas is reciprocated between the compression space 9 and the expansion space 10 via the regenerator 11 to extract the cold heat from the heat absorber 5, the high temperature side heat is limited in the limited space. The greater the amount of heat released by the exchanger 1a and the amount of heat absorbed by the low-temperature side heat exchanger 1b, the more the efficiency of pre-cooling or pre-heating of the working gas passing through the regenerator 11 is improved, so that the load on the regenerator 11 can be reduced accordingly. Thus, the refrigerating performance of the Stirling refrigerator 20 can be improved.
[0009]
[Problems to be solved by the invention]
However, in the above-described configuration of the conventional heat exchanger for a Stirling engine, the radiator 4 or the heat absorber 5 and the corrugated fin 2 are fixed by bonding or welding. Since it took time and effort, productivity was poor. Therefore, not only is it difficult to reduce the manufacturing cost, but also there is a problem that the quality of the finished product, that is, heat exchange performance tends to vary, and the stability and reliability of the product are lacking. Further, even if the performance of the Stirling refrigerator 20 deteriorates due to long-term use of the Stirling refrigerator 20, it cannot be removed and replaced. Therefore, there has been a problem in terms of increasing the economic burden on the user at the time of repair and recycling of resources in consideration of the global environment, that is, recycling.
[0010]
The present invention has been made in view of the above-mentioned conventional problems, and has high heat exchange performance with little variation in individual qualities, and a Stirling engine capable of reducing costs by simplifying a manufacturing method. It is an object to provide a heat exchanger for use. Another object of the present invention is to provide a heat exchanger for a Stirling engine suitable for recycling, in which parts can be removed and replaced as needed.
[0011]
[Means for Solving the Problems]
In order to achieve the above object, in the heat exchanger for a Stirling engine of the present invention,A cylindrical member;Concentrically inserted into the hollow part of the cylindrical memberWith elasticity that can expand and contract in the direction perpendicular to its axial directionA corrugated fin and the corrugated fin inserted concentrically into the hollow portion toward the cylindrical memberSpread it outCrimpingLetToforAnd a ring-shaped member. According to this configuration, the corrugated fin inserted into the cylindrical member and the contact portion between the cylindrical member and the corrugated fin are securely press-bonded by the ring-shaped member inserted inside thereof without being bonded or welded. Fixed.The ring-shaped member preferably has a length corresponding to the axial length of the corrugated fin.
[0012]
Note that one end of the side surface of the ring-shaped member may have a tapered structure that is tapered. According to this, it is easy to insert the ring-shaped member into the hollow portion.
[0013]
AndIn those used for the high-temperature side heat exchanger,If the coefficient of thermal expansion of the ring-shaped member is about the same as or larger than the coefficient of thermal expansion of the corrugated fin, even if the heat exchanger becomes high temperature due to a rise in ambient temperature, the ring-shaped member is Since pressure bonding is performed with a sufficient pressing force, there is no possibility that a gap is formed between the two.
[0014]
vice versa,In the one used for the low temperature heat exchanger,If the coefficient of thermal expansion of the ring-shaped member is about the same as or smaller than the coefficient of thermal expansion of the corrugated fin, even if the heat exchanger becomes low temperature due to a decrease in the peripheral temperature, the ring-shaped member is moved relative to the corrugated fin. Since pressure bonding is performed with a sufficient pressing force, there is no possibility that a gap is formed between the two.
[0015]
Further, when the ring-shaped member is formed of a material having high heat conductivity, a sufficient heat exchange effect can be obtained even with the ring-shaped member, and the heat exchange efficiency of the heat exchanger for a Stirling engine is improved.
[0016]
Further, the area of a portion of the corrugated fin that contacts the ring-shaped member and the cylindrical member may be increased. According to this, the amount of heat transferred to the ring-shaped member and the cylindrical member via the corrugated fin increases, and the heat exchange efficiency of the heat exchanger for a Stirling engine improves.
[0017]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the high-temperature side heat exchanger 1a using the radiator 4 (hereinafter, simply referred to as “heat exchanger”) will be described as an example. Selection, design change, etc. can be applied to the low-temperature side heat exchanger 1b using the heat absorber 5 as it is. Accordingly, unless otherwise specified, the term “radiator 4” may be replaced with the term “heat sink 5” in the following description. Further, the heat exchanger according to the present invention is different from the heat exchanger according to the above-described prior art only in the manufacturing method and structure, and therefore, in the following embodiments, the same reference numerals are given to members common to conventional products. The detailed description is omitted.
[0018]
<First embodiment>
FIG. 1A is a perspective view around a heat exchanger for a Stirling engine used in the first embodiment of the present invention. As shown in FIG. 1A, a heat exchanger 1a according to the present embodiment includes a corrugated fin 2 inserted concentrically into a hollow portion of a cylindrical radiator 4 having a predetermined length, and the hollow portion. And a ring 3 which is inserted concentrically into the corrugated fin 2 and crimps the corrugated fin 2 to the radiator 4 side. The outer diameter of the corrugated fin 2 is selected to be substantially equal to the inner diameter of the radiator 4, and the outer diameter of one of the rings 3 is set to be slightly larger than the inner diameter of the corrugated fin 2. The corrugated fins 2 are corrugated cylindrical members extending linearly at equal intervals along the axial direction all around the side surface, and have elasticity so that they can expand and contract in a direction perpendicular to the axial direction. are doing. Therefore, when the ring 3 is inserted as shown in the figure, the corrugated fin 2 is pushed and spread toward the radiator 4 due to its elasticity and pressed.
[0019]
Next, a manufacturing procedure of the heat exchanger 1a will be described with reference to FIG. First, the corrugated fin 2 is temporarily fixed to one end of the radiator 4. Reference numeral 16 denotes a ring fitting jig, which is a tapered columnar member. The outer diameter of the side surface of the jig 16 is selected to be substantially equal to the inner diameter of the ring 3, and when the ring 3 is inserted, the ring 3 is held halfway as shown in the drawing. In this state, the jig 16 is inserted into the radiator 4 from the tapered portion in the direction of the arrow. The ring 3 is fitted along the inner periphery of the side surface of the corrugated fin 2, and the corrugated fin 2 is pressed against the radiator 4 with a sufficient pressing force, and is fixed at a position where the tip is flush with the tip of the radiator 4. After confirming that the jig 16 has been removed, when only the jig 16 is pulled out in the direction opposite to the arrow, a heat exchanger 1a as shown in FIG. 1A is obtained.
[0020]
As the jig 16, for example, as shown in FIG. 3A, a slit 16 a extending in the axial direction is provided at several places on a cylindrical side surface, and a cap 16 b is put on an open end thereof. Can be suitably used. According to this, after the jig 16 is inserted into the radiator 4 as shown in FIG. 2 and the ring 3 is fixed at an appropriate position, the cap 16b is pinched and a force is applied inward, so that the jig 16 Since the outer diameter of the side surface is reduced and the holding of the ring 3 is released, only the jig 16 can be reliably pulled out without the ring 3 being pulled out together with the jig 16.
[0021]
The jig 16 may be formed of a hollow elastic body as shown in FIG. 3B. In this case, if air is sealed in the hollow portion of the jig 16, the external shape is maintained by air pressure, so that the jig 16 is not easily deformed even when an external force is applied. Accordingly, as described above, after the jig 16 is inserted into the radiator 4 and the ring 3 is fixed at an appropriate position, the air inside the jig 16 is evacuated and pinched to apply a force inside, thereby Since the tool 16 is easily deformed by the external force in the direction in which the outer diameter of the side surface is reduced and the ring 3 is released, the ring 3 is not pulled out together with the jig 16 and only the jig 16 can be reliably pulled out. it can.
[0022]
Meanwhile, the ring 3 used in the present embodiment is a cylindrical member whose outer diameter and thickness of the side surface are constant at any part in the vertical direction as shown in FIGS. 1 (b) and 1 (c). Therefore, since the corrugated fin 2 is pressed against the radiator 4 by the ring 3, the corrugated fin 2 can be fixed at an appropriate position in the radiator 4 without performing bonding or welding as in the related art. . This simplifies the assembling process of the heat exchanger 1a, so that manufacturing costs can be reduced.
[0023]
By pulling the ring 3 out of the radiator 4, the corrugated fin 2 can be removed at the same time. Therefore, when the Stirling refrigerator is used for a long period of time or the like, even if the corrugated fins 2 are damaged and the quality is deteriorated, the corrugated fins 2 can be easily replaced as needed, which is very economical. And a heat exchanger suitable for recycling can be realized. Further, the heat exchanger 1a used in the present embodiment has a local structure similar to that of the conventional heat exchanger shown in FIGS. 6A and 6B. There is almost no inferiority.
[0024]
<Second embodiment>
FIG. 4A is a perspective view of a heat exchanger for a Stirling engine used in the second embodiment of the present invention. In the first embodiment, the ring 3 has a straight cylindrical shape having the same cross-sectional shape at any part in the axial direction. Although the ring 3 has an outer diameter substantially equal to the inner diameter of the corrugated fin 2 as described above, the outer diameter is actually equal to the inner diameter of the corrugated fin 2 in order to secure the crimping and fixing of the corrugated fin 2. Is set slightly larger. In this case, when the ring 3 is fitted into the radiator 4 to which the corrugated fins 2 are temporarily fixed as described above, it is necessary to insert the ring 3 so that the corrugated fins 2 are pushed outward and spread. An excessive force is likely to be applied, and in some cases, the corrugated fin 2 may be deformed or damaged.
[0025]
Therefore, in the present embodiment, a ring 3 having a tapered structure 3a having a tapered structure at a predetermined length from its lower end is used as shown in FIGS. 3B and 3C. Accordingly, even if the outer diameter of the side surface of the portion of the ring 3 excluding the taper 3a is larger than the inner diameter of the corrugated fin 2, by inserting from the portion of the taper 3a having a relatively small outer diameter, the force is gradually gradually reduced at first. By applying a large force to the radiator 4, the ring 3 can be smoothly inserted into the radiator 4. Therefore, when the ring 3 is inserted, the jig for fitting the ring as in the first embodiment is not required, and an excessive force is hardly applied to the corrugated fin 2, and the corrugated fin 2 is damaged or deformed accordingly. The risk of doing so is reduced.
[0026]
<Third embodiment>
A third embodiment of the present invention will be described. In the first embodiment, the materials of the corrugated fins 2 and the ring 3 constituting the heat exchanger 1 are not particularly limited. However, in the case of the high-temperature side heat exchanger 1a, as shown in FIG. 6, the working gas flowing into the compression space 9 is preheated by the regenerator 11 to have a high temperature. In any case, the temperature of the high-temperature side heat exchanger 1a becomes high due to the heating through the working gas passing therethrough because the temperature has increased during the compression process. Therefore, when the ring 3 is made of a material having a smaller coefficient of thermal expansion than the corrugated fin 2 in FIG. 1A, a gap may be generated between the ring 3 and the fin 2 due to a difference in coefficient of thermal expansion when the temperature rises. There is. As a result, the ring 3 cannot sufficiently press the corrugated fin 2 on the radiator 4 side, and cannot secure a sufficient contact area between the corrugated fin 2 and the radiator 4. There is a possibility that the exchange performance will be reduced.
[0027]
Therefore, in the present embodiment, a material that is equal to or larger than the thermal expansion coefficient of the corrugated fin 2 is selected as the ring 3. As a result, even if the temperature rises, the rate of expansion of the ring 3 becomes equal to or greater than that of the corrugated fin 2, so that the corrugated fin 2 is pressed against the radiator 4 with a sufficient contact pressure without a gap. . As a result, a sufficient contact area between the two can be ensured, and the high-temperature side heat exchanger 1a having always stable heat exchange performance can be realized. It is preferable that the thermal expansion coefficient of the radiator 4 is equal to or smaller than that of the corrugated fin 2 for the same reason.
[0028]
<Fourth embodiment>
A fourth embodiment of the present invention will be described. In the first embodiment, the materials of the corrugated fins 2 and the ring 3 constituting the heat exchanger 1 are not particularly limited. However, in the case of the low-temperature side heat exchanger 1b,7As shown in the figure, the working gas flowing into the expansion space 10 is pre-cooled by the regenerator 11 and has a low temperature. On the other hand, the working gas flowing out of the expansion space 10 also has a lowered temperature during the expansion process. Even so, the low temperature side heat exchanger 1b becomes low temperature by cooling through the passing working gas. Therefore, when the ring 3 is made of a material having a higher coefficient of thermal expansion than the corrugated fin 2 in FIG. 1A, a gap may be formed between the ring 3 and the fin 2 due to a difference in coefficient of thermal expansion when the temperature decreases. There is. As a result, the ring 3 cannot sufficiently press the corrugated fin 2 against the heat sink 5 side, and cannot secure a sufficient contact area between the corrugated fin 2 and the heat sink 5. There is a possibility that the exchange performance will be reduced.
[0029]
Therefore, in the present embodiment, a material that is approximately equal to or smaller than the coefficient of thermal expansion of the corrugated fin 2 is selected as the ring 3. As a result, even if the temperature decreases, the rate of expansion of the ring 3 becomes equal to or smaller than that of the corrugated fin 2, so that the corrugated fin 2 is pressed against the heat absorber 5 with a sufficient contact pressure without a gap. . As a result, the contact area between the two can be sufficiently ensured, and the low-temperature side heat exchanger 1b having always stable heat exchange performance can be realized. The expansion coefficient of the heat absorber 5 is preferably the same as or larger than that of the corrugated fin 2 for the same reason.
[0030]
<Fifth embodiment>
A fifth embodiment of the present invention will be described. In the configuration of the heat exchanger 1a (see FIG. 1A) according to the present invention, since the working gas passes through the portion between the ring 3 and the radiator 4, heat exchange occurs not only in the corrugated fin 2 but also in the ring 3. Can be obtained. Therefore, in this embodiment, a material having high thermal conductivity such as copper or aluminum is selected for the ring 3. Thereby, the heat exchange performance of the heat exchanger 1a can be improved.
[0031]
<Sixth embodiment>
FIG. 5A is a perspective view around a heat exchanger according to a sixth embodiment of the present invention, and FIG. 5B is an enlarged view of a main part thereof. In each of the above embodiments, the structure of the corrugated portion of the side surface of the corrugated fin 2 has not been described in detail, but it is understood that the corrugated fin 2 is constituted by the V-shaped projection 2a and the groove 2b. 6 (b) and 6 (c). By the way, in the configuration of the heat exchanger 1a according to the present invention, the protruding portion 2a and the groove portion 2b of the corrugated fin 2 are in contact with the inner peripheral portion of the side surface of the radiator 4 and the outer peripheral portion of the side surface of the ring 3, respectively. However, when the contact area is small, the efficiency of heat radiation from the radiator 4 to the external space (in the case of the heat sink 5, absorption of heat from the external space) becomes insufficient, so that the heat exchanger has a stable heat exchange performance and, consequently, Stirling. Sufficient refrigerating capacity cannot be obtained from the refrigerator.
[0032]
Therefore, in the present embodiment, as shown in FIG. 5B, the shapes of the protruding portion 2a and the groove portion 2b of the corrugated fin 2 are set to be along the inner peripheral portion of the side surface of the radiator 4 and the outer peripheral portion of the side surface of the ring 3, respectively. Shape. As a result, the protruding portion 2a and the groove portion 2b come into contact with the radiator 4 and the ring 3 respectively in a relatively large area, and the heat exchange efficiency of the heat exchanger 1a via the corrugated fins 2 can be improved. A stable refrigerating capacity can be obtained from the refrigerator.
[0033]
In each of the above embodiments, the corrugated fin 2 is connected to the radiator 4 or the heat sink 4 by using only the pressure bonding by the ring 3 without welding or bonding the contact portion between the corrugated fin 2 and the radiator 4 or the heat sink 5. Although the case of fixing to the container 5 has been described, welding or bonding may be slightly applied to the contact portion as in the related art. In this case, the crimping / fixing of the corrugated fin 2 is further ensured.
[0034]
【The invention's effect】
As described above, according to the present invention, a corrugated fin concentrically inserted into a hollow portion of a cylindrical member, and a ring-shaped corrugated fin inserted concentrically into the hollow portion and crimping the corrugated fin toward the cylindrical member. The structure of the heat exchanger for a Stirling engine consisting of members eliminates the need for manual processes such as bonding and welding between a corrugated fin and a cylindrical member as in the prior art. The productivity can be improved, and the manufacturing cost of the heat exchanger can be reduced. In addition, the corrugated fin can be removed at the same time by pulling out the ring-shaped member from the cylindrical member. Therefore, when the Stirling refrigerator is used for a long period of time or the like, even if the corrugated fins are damaged and the quality is deteriorated, the corrugated fins 2 can be easily replaced as necessary, which is very economical. Yes, a heat exchanger suitable for recycling can be realized.
[0035]
By providing a tapered structure formed at one end of the side surface of the ring-shaped member with a tapered shape, even if the outer diameter of the side surface of the ring-shaped member excluding the taper is larger than the inner diameter of the corrugated fin, By inserting from a tapered portion having a relatively small diameter, a ring-shaped member can be smoothly inserted into the cylindrical member by gradually applying a large force with a small force at first. Therefore, when the ring-shaped member is inserted, a jig for inserting the ring is not required, and an excessive force is hardly applied to the corrugated fin, and the risk of the corrugated fin being damaged or deformed is reduced correspondingly.
[0036]
Further, as the ring-shaped member, a material similar to or larger than the thermal expansion coefficient of the corrugated fin is selected. As a result, even if the temperature around the high-temperature side heat exchanger rises, the rate of expansion of the ring-shaped member becomes equal to or larger than that of the corrugated fin, so that the corrugated fin has a cylindrical shape with sufficient contact pressure without gaps. It is crimped to the member. As a result, a sufficient contact area between the two can be ensured, and a heat exchanger having always stable heat exchange performance can be realized.
[0037]
In addition, a material that is equal to or smaller than the coefficient of thermal expansion of the corrugated fin is selected as the ring-shaped member. As a result, even if the temperature around the low-temperature side heat exchanger decreases, the rate of expansion of the ring-shaped member becomes equal to or smaller than that of the corrugated fin, so that the corrugated fin has a cylindrical shape with a sufficient contact pressure without a gap. It is crimped to the member. As a result, a sufficient contact area between the two can be ensured, and a heat exchanger having always stable heat exchange performance can be realized.
[0038]
Further, a material having high thermal conductivity such as copper or aluminum is selected as the ring-shaped member. Thereby, since a sufficient heat exchange effect can be obtained even with the ring-shaped member, the heat exchange performance of the heat exchanger can be improved.
[0039]
Furthermore, by increasing the area of the portion of the corrugated fin that contacts the ring-shaped member and the cylindrical member, the heat exchange efficiency due to the heat transfer through the corrugated fin can be improved, and the corrugated fin is stable from the Stirling refrigerator. Refrigeration capacity can be obtained.
[Brief description of the drawings]
FIG. 1A is a perspective view of an example of the vicinity of a heat exchanger for a Stirling engine according to a first embodiment of the present invention.
(B) It is a perspective view of the ring which comprises the heat exchanger.
(C) It is a side view of the ring.
FIG. 2 is a perspective view showing one process of manufacturing the heat exchanger.
FIG. 3A is a side view of an example of a ring fitting jig.
(B) It is a side sectional view of other examples of a ring fitting jig.
FIG. 4A is a perspective view of an example of the vicinity of a heat exchanger for a Stirling engine according to a second embodiment of the present invention.
(B) It is a perspective view of the ring which comprises the heat exchanger.
(C) It is a side view of the ring.
FIG. 5A is a perspective view of an example of the vicinity of a heat exchanger for a Stirling engine according to a sixth embodiment of the present invention.
(B) It is a principal part enlarged view of the heat exchanger.
FIG. 6 (a) is a perspective view around a conventional heat exchanger for a Stirling engine.
(B) It is a principal part enlarged view of an example of the heat exchanger.
(C) It is a principal part enlarged view of another example of the heat exchanger.
FIG. 7 is a schematic side sectional view of a free piston type Stirling refrigerator.
[Explanation of symbols]
1a High-temperature heat exchanger
1b Low-temperature heat exchanger
2 Corrugated fin
2a Projection
2b Groove
3 rings
4 radiator
5 Heat absorber
6 cylinder
7 Displacer
8 piston
9 compression space
10 Expansion space
11 Regenerator
12 Displacer rod
13 Spring
14 Adhesive
15 Welds
16 jig
20 Stirling refrigerator

Claims (6)

Wherein a cylindrical member is concentrically inserted into the hollow portion of the cylindrical member, and the corrugated fin having elasticity can expand and contract in its axial direction perpendicular to the direction, concentrically inserted into the hollow portion of the corrugated fin heat exchanger for the Stirling engine, characterized by comprising a ring-shaped member for which spread into the cylindrical member side Ru is crimped. A cylindrical member, a corrugated fin that is inserted concentrically into a hollow portion of the cylindrical member and has elasticity that can be expanded and contracted in the radial direction, and the corrugated fin that is inserted concentrically into the hollow portion and attaches the corrugated fin to the cylindrical member side. A heat exchanger for a Stirling engine, comprising: a ring-shaped member having a length in the axial center direction corresponding to the length of the corrugated fin for pressure bonding to a stirrup engine. The heat exchanger for a Stirling engine according to claim 1 or 2 , wherein one end of a side surface of the ring-shaped member has a tapered structure formed to be tapered. Be those used in the high-temperature side heat exchanger, claims 1 to 3 coefficients of thermal expansion of the ring-shaped member being characterized in that greater than comparable or even and the thermal expansion coefficient of the corrugated fin The heat exchanger for a Stirling engine according to any one of the above. Be those used in the low-temperature heat exchanger, claims 1 to 3, characterized in that the thermal expansion coefficient of the ring-shaped member is smaller than the thermal degree expansion coefficient the same or of the corrugated fin The heat exchanger for a Stirling engine according to any one of the above. The heat exchanger for a Stirling engine according to any one of claims 1 to 5, wherein an area of a portion of the corrugated fin that contacts the ring-shaped member and the cylindrical member is increased.

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