JP6284794B2 - Regenerator - Google Patents

Description

  The present invention relates to a regenerator for accumulating cold generated by Simon expansion of high-pressure refrigerant gas supplied from a compressor.

  A Gifford-McMahon (GM) refrigerator is known as a refrigerator that generates an extremely low temperature. The GM refrigerator changes the volume of the expansion space by reciprocating the displacer in the cylinder. The refrigerant gas expands in the expansion space by selectively connecting the expansion space, the discharge side of the compressor, and the intake side in response to the volume change. The cold of the refrigerant gas generated in the expansion space is transmitted to the cooling stage while being accumulated in the regenerator, reaches a desired cryogenic temperature, and cools the cooling target connected to the cooling stage (see Patent Document 1). .

JP 7-324832 A

  A regenerator material is used for the regenerator. When the refrigerant gas flows through the regenerator filled with the regenerator material, the refrigerant gas exchanges heat with the regenerator material. Here, the regenerator material filled in the regenerator is designed on the assumption that the flow rate of the refrigerant gas flowing through the regenerator is uniform regardless of the position in the regenerator. However, for example, when the refrigerant gas flows through the regenerator due to the influence of the channel resistance of the inner wall of the regenerator, the flow rate of the refrigerant gas flowing near the inner wall of the regenerator and the flow rate of the refrigerant gas flowing through the center of the regenerator May be different. In this case, the premise of the design of the regenerator material is broken, and the efficiency of the regenerator is reduced.

  An object of this invention is to provide the technique which improves the efficiency of the cool storage in a cryogenic refrigerator.

  In order to solve the above-described problem, a regenerator according to an aspect of the present invention includes a regenerator material that accumulates cold generated by expansion of a refrigerant gas, a cylindrical container that houses the regenerator material and through which refrigerant gas flows, And an insertion member that is accommodated in the container and has a uniform axial thickness of the container. The insertion member is provided with an opening serving as a refrigerant gas flow path at least in the outer peripheral portion, and the opening ratio of the entire insertion member is larger than the opening ratio of the central portion of the insertion member.

  According to the present invention, the efficiency of the regenerator in the cryogenic refrigerator can be improved.

It is a figure which shows typically an example of the regenerator type refrigerator which concerns on embodiment. It is a schematic diagram for demonstrating the flow velocity distribution of the refrigerant gas which flows through the 2nd regenerator which concerns on embodiment. It is a figure which shows typically the shape of the insertion member which concerns on embodiment. FIGS. 4A to 4B are diagrams illustrating the aperture ratio of the insertion member according to the embodiment. Fig.5 (a)-(b) is a figure which shows typically another shape of the insertion member which concerns on embodiment. It is a figure which shows typically another shape of the insertion member which concerns on embodiment. FIGS. 7A and 7B are diagrams for explaining changes in the opening ratio in the circumferential direction at the outer peripheral portion of the insertion member according to the embodiment. FIGS. 8A to 8B are conceptual diagrams illustrating changes in the aperture ratio of the insertion member according to the embodiment.

  Hereinafter, embodiments for carrying out the present invention will be described with reference to the accompanying drawings.

  FIG. 1 is a diagram schematically illustrating an example of a regenerator refrigerator 1 according to an embodiment. The regenerator type refrigerator 1 according to the embodiment is a Gifford McMahon (GM) type cryogenic refrigerator that uses helium gas as a refrigerant gas, for example. As shown in FIG. 1, the regenerator type refrigerator 1 includes a first displacer 2 and a second displacer 3 connected to the first displacer 2 in the longitudinal direction. The first displacer 2 and the second displacer 3 are connected via, for example, a pin 4, a connector 5, and a pin 6.

  The first cylinder 7 and the second cylinder 8 are integrally formed, and each has a high temperature end and a low temperature end. The low temperature end of the first cylinder 7 and the high temperature end of the second cylinder 8 are connected at the bottom of the first cylinder 7. The second cylinder 8 is formed in a form extending in the same axial direction as the first cylinder 7, and is a cylindrical member having a smaller diameter than the first cylinder 7. The 1st cylinder 7 is a cylindrical container which accommodates the 1st displacer 2 so that a reciprocation is possible in a longitudinal direction. The second cylinder 8 is a cylindrical container that accommodates the second displacer 3 so as to be reciprocally movable in the longitudinal direction.

  For example, stainless steel is used for the first cylinder 7 and the second cylinder 8 in consideration of strength, thermal conductivity, helium blocking ability, and the like. The outer peripheral portion of the second displacer 3 is a cylinder made of metal such as stainless steel. On the outer peripheral surface of the second displacer 3, a film of an abrasion resistant resin such as a fluororesin may be formed.

  A scotch yoke mechanism (not shown) that reciprocates the first displacer 2 and the second displacer 3 is provided at the high temperature end of the first cylinder 7. The first displacer 2 and the second displacer 3 reciprocate along the first cylinder 7 and the second cylinder 8, respectively. The first displacer 2 and the second displacer 3 each have a high temperature end and a low temperature end.

  The first displacer 2 is a container having a cylindrical outer peripheral surface. For the first displacer 2, for example, a phenol resin with cloth is used from the viewpoint of specific gravity, strength, thermal conductivity, and the like. The inside of the first displacer 2 is filled with a first cold storage material in which, for example, metal (metal mesh) processed into a mesh shape is stacked. The internal volume of the first displacer 2 functions as the first regenerator 9. A rectifier 10 is installed in the upper part of the first regenerator 9, and a rectifier 11 is installed in the lower part. A first opening 13 through which refrigerant gas flows from the room temperature chamber 12 to the first displacer 2 is formed at the high temperature end of the first displacer 2.

  The room temperature chamber 12 is a space formed by the first cylinder 7 and the high temperature end of the first displacer 2. The room temperature chamber 12 changes in volume as the first displacer 2 reciprocates. The room temperature chamber 12 is connected to a common supply / exhaust pipe among the pipes connecting the intake and exhaust systems including the compressor 14, the supply valve 15, and the return valve 16. In addition, a seal 17 is attached between the portion of the first displacer 2 from the high temperature end and the first cylinder 7.

  A second opening 19 is formed at the low temperature end of the first displacer 2 for introducing the refrigerant gas into the first expansion space 18 via the first clearance C1. The first expansion space 18 is a space formed by the first cylinder 7 and the first displacer 2. The volume of the first expansion space 18 changes as the first displacer 2 reciprocates. A first cooling stage 20 that is thermally connected to an object to be cooled (not shown) is disposed at a position corresponding to the first expansion space 18 in the outer periphery of the first cylinder 7. The first cooling stage 20 is cooled by the refrigerant gas passing through the first clearance C1.

The second displacer 3 has a cylindrical outer peripheral surface. The inside of the second displacer 3 is divided into two stages in the axial direction with a rectifier 21 at the upper end, a rectifier 22 at the lower end, and a partition member 23 located in the middle between the upper and lower sides. Of the internal volume of the second displacer 3, the high temperature side region 24 higher than the partition member 23 is filled with a second cold storage material made of a nonmagnetic material such as lead or bismuth. The low temperature side region 25 on the low temperature (lower stage) side of the partition member 23 is filled with a third cold storage material made of a magnetic material such as HoCu ₂ , which is different from the high temperature side region 24. Lead, bismuth, HoCu _{2 and the} like are formed in a spherical shape, and a plurality of spherical formations are gathered to form a cold storage material. The partition member 23 is a filter that restricts the passage of the second cold storage material and the third cold storage material in order to prevent the cold storage material in the high temperature region 24 and the cold storage material in the low temperature region 25 from mixing. (Not shown). The high temperature side region 24 and the low temperature side region 25, which are internal volumes of the second displacer 3, function as the second regenerator 34. The first expansion space 18 and the high temperature end of the second displacer 3 are communicated with each other through a communication path around the connector 5. Refrigerant gas flows from the first expansion space 18 to the second regenerator 34 through this communication path.

  A third opening 27 is formed at the low temperature end of the second displacer 3 for allowing the refrigerant gas to flow through the second expansion space 26 via the second clearance C2. The second expansion space 26 is a space formed by the second cylinder 8 and the second displacer 3. The volume of the second expansion space 26 changes as the second displacer 3 reciprocates. The second clearance C <b> 2 is formed by the low temperature end of the second cylinder 8 and the second displacer 3.

  A second cooling stage 28 that is thermally connected to the object to be cooled is disposed at a position corresponding to the second expansion space 26 on the outer periphery of the second cylinder 8. The second cooling stage 28 is cooled by the refrigerant gas passing through the second clearance C2.

  The first displacer 2 and the second displacer 3 may include a lid portion 29 and a lid portion 30 at the low temperature end, respectively. The lid portion 29 and the lid portion 30 have a two-stage cylindrical shape from the viewpoint of joining with the displacer body. The lid portion 29 is fixed to the first displacer 2 by a press-fit pin 31, and the lid portion 30 is fixed to the second displacer 3 by a press-fit pin 32.

  The second regenerator 34 includes a first insertion member 35 a that adjusts the flow velocity distribution of the refrigerant gas flowing through the high temperature side region 24, and a second insertion member 35 b that adjusts the flow velocity distribution of the refrigerant gas flowing through the low temperature side region 25. Hereinafter, when the first insertion member 35a and the second insertion member 35b are not distinguished, they are collectively referred to as “insertion member 35”. Details of the insertion member 35 will be described later.

  Next, the operation of the regenerator type refrigerator 1 according to the embodiment will be described. At a certain point in the refrigerant gas supply process, the first displacer 2 and the second displacer 3 are located at the bottom dead center of the first cylinder 7 and the second cylinder 8. When the supply valve 15 is opened at the same time or at a slightly shifted timing, high-pressure helium gas (for example, 2.2 MPa helium gas) is supplied into the first cylinder 7 from the supply / discharge common pipe via the supply valve 15. Then, the air flows into the first regenerator 9 inside the first displacer 2 from the first opening 13 located at the upper part of the first displacer 2. The high-pressure helium gas that has flowed into the first regenerator 9 is cooled by the first regenerator material and enters the first expansion space 18 via the second opening 19 and the first clearance C1 that are located below the first displacer 2. Supplied.

  The high-pressure helium gas supplied to the first expansion space 18 flows into the second regenerator 34 inside the second displacer 3 through the communication passage around the connector 5. The high-pressure helium gas that has flowed into the second regenerator 34 is supplied to the second expansion space 26 through the third opening 27 and the second clearance that are positioned below the second displacer 3 while being cooled by the second regenerator material. Is done.

  In this way, the first expansion space 18 and the second expansion space 26 are filled with the high-pressure helium gas, and the supply valve 15 is closed. At this time, the first displacer 2 and the second displacer 3 are located at the top dead center in the first cylinder 7 and the second cylinder 8. When the return valve 16 is opened at the same time or slightly shifted timing, the refrigerant gas in the first expansion space 18 and the second expansion space 26 is decompressed and expanded, and low-pressure helium gas (for example, 0.8 MPa helium). Gas). At this time, cold is generated by the expansion of the refrigerant gas. The helium gas in the first expansion space 18 that has become low temperature due to expansion absorbs the heat of the first cooling stage 20 through the first clearance C1. The helium gas in the second expansion space 26 absorbs the heat of the second cooling stage 28 through the second clearance C2.

  The first displacer 2 and the second displacer 3 move toward the bottom dead center, and the volumes of the first expansion space 18 and the second expansion space 26 decrease. The helium gas in the second expansion space 26 is returned to the first expansion space 18 via the second clearance C2, the third opening 27, the second regenerator 34, and the communication path. Further, the helium gas in the first expansion space 18 is returned to the suction side of the compressor 14 through the second opening 19, the first regenerator 9, and the first opening 13. In that case, the 1st cool storage material, the 2nd cool storage material, and the 3rd cool storage material are cooled with refrigerant gas. That is, the 1st cool storage material, the 2nd cool storage material, and the 3rd cool storage material accumulate cold produced by expansion of refrigerant gas. This process is defined as one cycle, and the regenerator type refrigerator 1 cools the first cooling stage 20 and the second cooling stage 28 by repeating this cooling cycle.

  Next, the insertion member 35 according to the embodiment will be described in more detail.

  FIG. 2 is a schematic diagram for explaining the flow velocity distribution of the refrigerant gas flowing through the second regenerator 34 according to the embodiment, and is a diagram illustrating the flow velocity distribution when the insertion member 35 is not provided. As described above, the second regenerator 34 accommodates a plurality of formations formed in a spherical shape as a regenerator material.

  In FIG. 2, arrows indicated by reference numerals 40 and 41 are vectors indicating the flow rate of the refrigerant gas. Specifically, the vector 40 a, the vector 40 b, the vector 40 c, the vector 40 d, the vector 40 e, and the vector 40 f indicate the flow velocity distribution of the refrigerant gas that flows on the high temperature end side of the second regenerator 34. Further, the vector 41a, the vector 41b, the vector 41c, the vector 41d, the vector 41e, and the vector 41f indicate the flow velocity distribution of the refrigerant gas that flows on the low temperature end side of the second regenerator 34.

  In FIG. 2, the lengths of vectors 40c and 40d indicating the flow velocity at the center of the second regenerator 34 on the high temperature end side, and the lengths of vectors 40a and 40f indicating the flow velocity near the inner wall of the second regenerator 34 are shown. Are equivalent. This indicates that the flow velocity distribution of the refrigerant gas is uniform at the high temperature side end of the second regenerator 34 regardless of the position of the second regenerator 34.

  On the other hand, the length of the vector 41c and vector 41d indicating the flow velocity at the central portion on the low temperature end side of the second regenerator 34 is longer than the length of the vector 41a and vector 41f indicating the flow velocity near the inner wall of the second regenerator 34. Also long. This indicates that the flow velocity distribution of the refrigerant gas is not uniform at the low temperature side end of the second regenerator 34.

  The regenerator material accommodated in the second regenerator 34 is a metal sphere formed so that the radii are the same. For this reason, it can be said that the flow path resistance resulting from the regenerator material in the second regenerator 34 is uniform regardless of the position of the second regenerator 34. On the other hand, the flow path resistance of the refrigerant gas caused by the inner wall of the second regenerator 34 naturally exists only on the inner wall of the second regenerator 34 and does not exist in the center of the second regenerator 34. For this reason, the flow path resistance in the vicinity of the inner wall of the second regenerator 34 is larger than the flow path resistance at the center of the second regenerator 34.

  As a result, as the refrigerant gas flows through the second regenerator 34 from the high temperature end toward the low temperature end, the flow velocity near the inner wall of the second regenerator 34 becomes smaller than the flow velocity at the center of the second regenerator 34. . Therefore, the flow velocity distribution of the refrigerant gas is not uniform at the low temperature side end of the second regenerator 34, and has a hemispherical or rotary parabolic shape with a convex portion on the low temperature end side.

  The second regenerator 34 is substantially uniformly filled with a regenerator material having a substantially uniform shape. Therefore, it can be said that the heat exchange efficiency between the refrigerant gas and the cold storage material depends on the flow rate of the refrigerant gas. Specifically, the greater the flow rate of the refrigerant gas flowing through the regenerator material, the greater the efficiency of heat exchange with the regenerator material. For this reason, on the low temperature end side of the second regenerator 34, the temperature of the regenerator material present at the center of the second regenerator 34 is higher than the temperature of the regenerator material present near the inner wall of the second regenerator 34. . As a result, a temperature gradient of the regenerator material is created in a direction perpendicular to the long axis of the second regenerator 34. If it does so, a heat transfer will arise from the cool storage material which exists in the center part of the 2nd cool storage device 34 toward the cool storage material which exists near the inner wall of the 2nd cool storage device 34, and it becomes entropy loss. Therefore, when the flow velocity distribution of the refrigerant gas flowing through the second regenerator 34 is not uniform, the efficiency of the second regenerator 34 decreases. In addition, when the refrigerant gas flows from the low temperature end toward the high temperature end, the heat moves in the direction opposite to the above.

  Based on the above, the second regenerator 34 according to the embodiment includes an insertion member 35 for making the flow velocity distribution of the refrigerant gas flowing through the second regenerator 34 uniform.

  FIG. 3 is a diagram schematically illustrating the shape of the insertion member 35 according to the embodiment. The insertion member 35 is inserted into the second regenerator 34 that is a cylindrical container. For this reason, the insertion member 35 is formed in a disk shape so as to fit in the inner wall of the second regenerator 34. The insertion member 35 is formed so that the axial thickness of the second regenerator 34 is uniform when inserted into the second regenerator 34. The insertion member 35 is also provided so that the opening 36 serving as a refrigerant gas flow path penetrates from the high temperature end side to the low temperature end side when inserted into the second regenerator 34. For example, the insertion member is a plate-like member having a plurality of openings. In FIG. 3, only one opening 36 is denoted by a symbol to avoid complication. However, all of the shapes shown in white in FIG. The same applies to FIGS. 4 and 5 described later.

  In FIG. 3, the black circle indicated by reference numeral 37 is the center 37 of the insertion member 35. As shown in FIG. 3, the insertion member 35 is not provided with an opening 36 in the central region including the center 37, and at least one opening 36 is provided on the outer periphery of the insertion member 35.

  Here, the “outer peripheral portion” of the insertion member 35 is an annular region surrounded by two concentric circles having the center 37 of the insertion member 35 as a common center. In the annular region constituting the outer peripheral portion of the insertion member 35, the outer circle may coincide with the outer periphery of the insertion member 35. Further, the “inner peripheral portion” of the insertion member 35 is a region surrounded by an inner circle in an annular region constituting the outer peripheral portion. It can be said that the inner peripheral portion of the insertion member 35 is a region of the central portion of the insertion member 35 including the center 37 of the insertion member 35.

  FIGS. 4A to 4B are diagrams illustrating the aperture ratio of the insertion member 35 according to the embodiment. More specifically, FIG. 4A is a diagram for explaining the overall aperture ratio of the insertion member 35 shown in FIG. 3, and FIG. 4B is an aperture ratio at the center of the insertion member 35 shown in FIG. FIG.

  As shown in FIG. 4A, the opening ratio of the entire insertion member 35 is expressed as a percentage of the total area Sb of the area of the opening 36 in the upper surface portion of the insertion member 35 with respect to the total surface area Sa of the upper surface portion of the insertion member 35. It is. In FIG. 4A, a hatched region is a region that is a target for calculating the aperture ratio of the entire insertion member 35.

  On the other hand, the opening ratio at the center of the insertion member 35 is the opening ratio in the circular region 38 centered on the center 37 of the insertion member 35. That is, the aperture ratio at the center of the insertion member 35 is expressed as a percentage of the total area Sd of the areas of the openings 36 in the circular area 38 with respect to the area Sc of the circular area 38. A region indicated by diagonal lines in FIG. 4B is a circular region 38. Therefore, in FIG. 4A, the circular region 38 coincides with the entire upper surface portion of the insertion member 35. Note that the circular region 38 illustrated in FIG. 4B is an example of the inner peripheral portion of the insertion member 35 described above.

  As shown in FIGS. 3 and 4 (a)-(b), the insertion member 35 is configured such that the density of the opening 36 in the outer periphery of the opening 36 is greater than the density of the opening 36 in the center. Is formed. For this reason, in the insertion member 35, the opening ratio of the entire insertion member 35 is larger than the opening ratio of the central portion of the insertion member 35. That is, the insertion member 35 has a larger number of openings 36 in the outer peripheral portion than the central portion, and the refrigerant gas can easily flow. Accordingly, when the insertion member 35 is inserted into the second regenerator 34, the refrigerant gas has a smaller flow resistance of the refrigerant gas on the inner wall side of the second regenerator 34 than on the center portion. As a result, the flow velocity distribution of the refrigerant gas flowing through the second regenerator 34 approaches uniformly.

  3 and 4 (a)-(b) show an insertion member 35 provided with a plurality of openings 36 and having the same shape. The shape of the opening 36 provided in the insertion member 35 may not be the same, and the size and shape may be different.

  Fig.5 (a)-(b) is a figure which shows typically another shape of the insertion member 35 which concerns on embodiment. Specifically, FIGS. 5A and 5B are views showing an insertion member 35 having openings 36 having the same shape but different sizes.

  The insertion member 35 shown in FIG. 5 does not have an opening 36 near the center 37. Further, in the insertion member 35 shown in FIG. 5, the size of the opening 36a provided in the outer peripheral portion is larger than the size of the opening 36b provided in the inner side thereof. Here, FIG. 5A shows the entire insertion member 35. FIG. 5B shows the center portion of the insertion member 35. The insertion member 35 shown in FIGS. 5A and 5B also has an opening ratio of the entire insertion member 35 larger than the opening ratio of the central portion of the insertion member 35, similarly to the insertion member 35 shown in FIG. 3.

  FIG. 6 is a diagram schematically showing still another shape of the insertion member 35 according to the embodiment. Specifically, FIG. 6 is a view showing an insertion member 35 having openings 36 having different sizes and shapes.

  The insertion member 35 shown in FIG. 6 also has no opening 36 in the vicinity of the center 37. Further, in the insertion member 35 shown in FIG. 6, the size of the opening 36a provided on the outer peripheral portion is larger than that of the opening 36b provided on the inner side. As with the insertion member 35 shown in FIGS. 3 and 4, the insertion member 35 shown in FIG. 6 has a larger opening ratio than the central portion of the insertion member 35.

  As described above, the insertion member 35 according to the embodiment is configured such that the aperture ratio is greater at the outer peripheral portion than at the central portion. For this reason, the flow path resistance of the central portion of the insertion member 35 is greater than that of the outer peripheral portion, and the refrigerant gas passing through the insertion member 35 has a greater flow rate reduction method in the central portion than in the outer peripheral portion. Thereby, by inserting the insertion member 35, the flow rate of the refrigerant gas flowing through the second regenerator 34 can be made uniform regardless of the position inside the second regenerator 34.

  Here, from the viewpoint of making the flow rate of the refrigerant gas flowing through the second regenerator 34 uniform regardless of the position inside the second regenerator 34, the opening ratio of the insertion member 35 is in the circumferential direction of the insertion member 35. Is preferably constant.

  FIGS. 7A and 7B are diagrams for explaining changes in the opening ratio in the circumferential direction at the outer peripheral portion of the insertion member 35 according to the embodiment. In FIG. 7A, the first partial region 39 a is an annular region surrounded by concentric circles 42 a and 42 b having the center 37 of the insertion member 35 as a common center, that is, a part of the outer peripheral portion of the insertion member 35. . In FIG. 7B, the second partial region 39b is a part of an annular region surrounded by concentric circles 42a and 42b having the center 37 of the insertion member 35 as a common center. This is a region different from the first partial region 39a shown. 7A to 7B, the concentric circle 42a may coincide with the outer periphery of the insertion member 35. The first partial region 39a and the second partial region 39b are determined so as to include at least one opening 36.

  Since the first partial region 39a and the second partial region 39b are different regions, the aperture ratios are also different. However, the insertion member 35 according to the embodiment is configured such that the openings 36 appear periodically in the circumferential direction. For this reason, even if the first partial region 39a and the second partial region 39b are different regions, the difference in aperture ratio is within a predetermined range R.

  FIGS. 8A to 8B are conceptual diagrams showing changes in the aperture ratio of the insertion member 35 according to the embodiment. More specifically, FIG. 8A is a graph showing a change tendency of the aperture ratio along the radial direction of the insertion member 35, and FIG. 8B is a graph of the aperture ratio along the circumferential direction of the insertion member 35. It is a graph which shows the tendency of a change. FIGS. 8A and 8B show a case where the aperture ratio is derived by setting a partial region including at least one opening 36.

  As described above, in the insertion member 35 according to the embodiment, the density of the openings 36 in the outer peripheral portion is larger than the density of the openings 36 in the inner peripheral portion. For this reason, as shown to Fig.8 (a), the aperture ratio of the insertion member 35 becomes so large that it leaves | separates from a center part toward radial direction.

  On the other hand, the insertion member 35 according to the embodiment is configured such that the openings 36 appear periodically in the circumferential direction. For this reason, as described with reference to FIGS. 7A and 7B, when the aperture ratio of the insertion member 35 is the same in the radial direction, the difference in aperture ratio is within a predetermined range even if it moves in the circumferential direction. Fits in R. Thus, the insertion member 35 has a difference in flow path resistance along the circumferential direction within a certain range. Therefore, the refrigerant gas passing through the insertion member 35 has a rate of decrease in the flow rate within a certain range R regardless of the position in the circumferential direction of the insertion member 35. Therefore, by inserting the insertion member 35, the flow rate of the refrigerant gas flowing through the second regenerator 34 can be made uniform regardless of the position inside the second regenerator 34.

  When the flow velocity distribution of the refrigerant gas flowing through the second regenerator 34 approaches uniformly, the temperature distribution of the regenerator material also becomes uniform in the direction perpendicular to the major axis of the second regenerator 34. Thereby, regarding the regenerator material accommodated in the second regenerator 34, the movement of heat in the direction perpendicular to the major axis of the second regenerator 34 is suppressed, and the loss of entropy can also be suppressed. Accordingly, the efficiency of the second regenerator 34 can be improved, and as a result, the refrigerating performance of the regenerator refrigerator 1 including the second regenerator 34 can be improved.

  By the way, when the insertion member 35 is inserted into the second regenerator 34, the regenerator material that can be filled in the second regenerator 34 is reduced by the volume of the insertion member 35. The decrease in the regenerator material charged in the second regenerator 34 can also cause a decrease in the refrigerating performance of the regenerator refrigerator 1 including the second regenerator 34.

  Therefore, the insertion member 35 according to the embodiment may have the function as the partition member 23 described above, and may be inserted into the second regenerator 34 instead of the partition member 23. As described above, the second regenerator 34 accommodates the second regenerator material and the third regenerator material made of a material different from the second regenerator material in the high temperature side region 24 and the low temperature side region 25, respectively. Filters that restrict the passage of the second and third regenerator materials are provided at both ends of the opening 36 of the insertion member 35, and are inserted at the boundary between the first and second regenerator materials. Thereby, the insertion member 35 can give the function of the partition member 23 mentioned above.

  Since the partition member 23 is conventionally accommodated in the second regenerator 34, even if the partition member 23 is replaced with the insertion member 35, the regenerator material that can be filled in the second regenerator 34 does not decrease as compared with the conventional case. . When the insertion member 35 is thicker than the conventional partition member 23, the cool storage material which can be filled in the 2nd cool storage 34 by the difference will decrease from the past. However, the influence can be suppressed rather than inserting the insertion member 35 into the second regenerator 34 in addition to the partition member 23. As a result, the flow rate distribution of the refrigerant gas flowing through the second regenerator 34 can be made closer to uniform while maintaining the amount of the regenerator material that can be charged in the second regenerator 34. Alternatively, the insertion member 35 may be disposed at a position adjacent to the partition member 23.

  As described above, according to the second regenerator 34 of the present invention, the efficiency of the regenerator can be improved.

  Although the preferred embodiments of the present invention have been described in detail above, the present invention is not limited to the above-described embodiments, and various modifications and substitutions are made to the above-described embodiments without departing from the scope of the present invention. be able to.

  In the above description, the case where the insertion member 35 is inserted into the second regenerator 34 has been mainly described. The insertion member 35 may be inserted into the first regenerator 9 instead of or in addition to the second regenerator 34. In this case, the insertion member 35 may be appropriately enlarged and used in accordance with the size of the inner peripheral portion of the first regenerator 9. Since the efficiency of the first regenerator 9 can be improved, the refrigerating performance of the regenerator type refrigerator 1 can be further improved.

  In the above-described regenerator type refrigerator, the case where the number of stages is two is shown, but the number of stages may be one, or may be appropriately selected to be three or more. In the embodiment, the example in which the regenerator type refrigerator is a displacer type GM refrigerator has been described, but the present invention is not limited thereto. For example, the present invention can be applied to a pulse tube type GM refrigerator, a Stirling refrigerator, a Solvay refrigerator, and the like.

  DESCRIPTION OF SYMBOLS 1 Regenerator type refrigerator, C1 1st clearance, 2 1st displacer, C2 2nd clearance, 3 2nd displacer, 4 pins, 5 connectors, 6 pins, 7 1st cylinder, 8 2nd cylinder, 9 1st cool storage 10, 11 rectifier, 12 room temperature chamber, 13 first opening, 14 compressor, 15 supply valve, 16 return valve, 17 seal, 18 first expansion space, 19 second opening, 20 first cooling stage, 21, 22 Rectifier, 23 Partition member, 24 High temperature side region, 25 Low temperature side region, 26 Second expansion space, 27 Third opening, 28 Second cooling stage, 29, 30 Lid, 31, 32 Press-fit pin, 34 Second cold storage , 35 insertion member, 36 opening, 37 center, 38 circular region, 39a first Partial region, 39b Second partial region.

Claims (3)

A regenerator material that accumulates the cold produced by the expansion of the refrigerant gas;
A cylindrical container that houses the cold storage material and through which refrigerant gas flows;
An insertion member that is housed in the container and has a uniform axial thickness of the container,
Said insert member has an opening serving as the refrigerant gas flow path is provided at least on the outer peripheral portion, the insertion member across the aperture ratio is much larger than the aperture ratio of the center portion of the insertion member,
Regenerator said insert member includes a plurality of openings of the same shape, the density of the openings at the outer peripheral portion, characterized in size Ikoto than the density of the openings in the inner peripheral portion.   The insertion member has an opening ratio in a first partial region including at least one opening in an outer peripheral portion of the insertion member, and an opening in a second partial region different from the first partial region in the outer peripheral portion of the insertion member. The regenerator according to claim 1, wherein an opening ratio is provided so that a difference from the rate falls within a predetermined range. The cold storage material includes a first cold storage material and a second cold storage material made of a material different from the first cold storage material,
The container accommodates the first cold storage material and the second cold storage material in different regions,
The insertion member includes a filter that restricts the first cool storage material and the second cool storage material from passing through the opening, and is inserted into a boundary between the first cool storage material and the second cool storage material. The regenerator according to claim 1 or 2 , wherein

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