JP2013217517A - Regenerative refrigerator and regenerator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a regenerative refrigerator and a regenerator which can increase freezing performance more effectively based on the transmission of a cold temperature in an axial direction.SOLUTION: A regenerative refrigerator 1 includes a regenerator 24 which includes a regenerative member and extends in an axial direction and a heat transfer member 33 which is adjacent to the regenerative member and extends in the axial direction.

Description

  The present invention relates to a regenerator type refrigerating machine and a regenerator type which generate a desired cryogenic cold by generating a Simon expansion using a high-pressure refrigerant gas supplied from a compression device and accumulating the cold by a regenerator. The present invention relates to a regenerator used in a refrigerator.

  There exists a thing of patent document 1 as a regenerator type refrigerator, for example. The displacer-type regenerator refrigerator generates cold by expanding the refrigerant gas in the expansion space while reciprocating the displacer inside the cylinder. Further, the pulse tube type regenerator type refrigerator expands the refrigerant gas in the expansion space while reciprocating the gas piston in the pulse tube to generate cold. 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 freezes the object to be cooled connected to the cooling stage.

JP 2008-224161 A

  It is an object of the present invention to provide a regenerator type refrigerator and a regenerator that can more effectively enhance the refrigerating performance.

  One embodiment of the present invention is a regenerator type refrigerator. This regenerator type refrigerator includes a regenerator that includes a regenerator and extends in the axial direction, and a heat transfer member that extends adjacent to the regenerator and extends in the axial direction.

  Another aspect of the present invention is a regenerator. The regenerator includes a heat transfer member that includes the regenerator material and extends in the axial direction and extends in the axial direction adjacent to the regenerator material.

  According to the regenerator type refrigerator and the regenerator of the present invention, heat can be transmitted from the high temperature end to the low temperature end of the heat transfer member, and the efficiency of the refrigerator can be increased.

It is a schematic diagram shown about one Embodiment of the regenerator type refrigerator 1 and the regenerator 24 of Example 1 which concerns on this invention. It is a schematic diagram which shows the cross section perpendicular | vertical to the axial direction and the cross section containing an axial direction of the heat-transfer member 33 which the regenerator type refrigerator 1 of Example 1 contains, respectively. It is a schematic diagram shown about other embodiment of the regenerator type refrigerator 1 and the regenerator 24 of Example 1. FIG. It is a schematic diagram shown about other embodiment of the regenerator type refrigerator 1 and the regenerator 24 of Example 1. FIG. It is a schematic diagram shown about other embodiment of the regenerator type refrigerator 1 and the regenerator 24 of Example 1. FIG. It is a schematic diagram shown about one Embodiment of the regenerator type refrigerator 41 and the regenerator 24 of Example 2 which concerns on this invention. It is a schematic diagram shown about other embodiment of the regenerator type refrigerator 41 and the regenerator 24 of Example 2. FIG. It is a schematic diagram shown about one embodiment of the regenerator type refrigerator 51 and the regenerator 53 of Example 3 according to the present invention. It is a schematic diagram shown about one Embodiment of the regenerator type refrigerator 101 and the regenerator 103 of Example 4 which concerns on this invention.

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

  The regenerator type refrigerator 1 of the first 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 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 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 first cylinder 7 accommodates the first displacer 2 so as to be capable of reciprocating in the longitudinal direction, and the second cylinder 8 accommodates the second displacer 3 so as to be capable of reciprocating 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. A film of an abrasion-resistant resin such as a fluororesin may be formed on the outer peripheral surface of a metal cylinder such as stainless steel of the second displacer 3.

  A high temperature end of the first cylinder 7 is provided with a scotch yoke mechanism (not shown) for reciprocatingly driving the first displacer 2 and the second displacer 3. The first displacer 2 and the second displacer 3 are respectively connected to the first cylinder 7 and the second displacer 3. It reciprocates along the second cylinder 8.

  The first displacer 2 has a cylindrical outer peripheral surface, and the first displacer 2 is filled with a first cool storage material. 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, and the volume changes 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. Further, a seal 17 is mounted 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. The first expansion space 18 is a space formed by the first cylinder 7 and the first displacer 2, and the volume 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 on the outer periphery of the first cylinder 7, and the first cooling stage 20 has a first clearance. It is cooled by the refrigerant gas passing through.

  The second displacer 3 has a cylindrical outer peripheral surface, and the inside of the second displacer 3 has two stages in the axial direction with the rectifier 21 at the upper end, the rectifier 22 at the lower end, and the partition member 23 located in the middle between the upper and lower sides. It is divided into. 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 regenerator 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 material 23 is filled with a cold storage material different from the high temperature side region 24, for example, a second cold storage material of magnetic material such as HoCu2. The partition material 23 prevents the cold storage material in the high temperature region 24 and the cold storage material in the low temperature region 25 from mixing. The high temperature side region 24 and the low temperature side region 25 which are internal volumes of the second displacer 3 function as a second regenerator. 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. The refrigerant gas flows from the first expansion space 18 to the second regenerators 24 and 25 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. The second expansion space 26 is a space formed by the second cylinder 8 and the second displacer 3, and the volume changes as the second displacer 3 reciprocates. The second clearance is formed by the low temperature end portion of the second cylinder 8 and the second displacer 3.

  A second cooling stage 28 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, and the second cooling stage 28 passes through the second clearance. Cooled by the refrigerant gas.

  For the first displacer 2, for example, cloth-containing phenol is used from the viewpoint of specific gravity, strength, thermal conductivity, and the like. A 1st cool storage material is comprised, for example with a wire mesh. The second displacer 3 is configured by sandwiching a spherical second regenerator material such as lead or bismuth in the axial direction with a felt and a wire mesh. Note that, as described above, the internal volume of the second displacer 3 may be divided into a plurality of regions by a partition material.

  The first displacer 2 and the second displacer 3 may include heat exchange units 29 and 30 at low temperature ends, respectively. The heat exchange parts 29 and 30 have a two-stage cylindrical shape from the viewpoint of joining with the displacer body. The heat exchange unit 29 is fixed to the first displacer 2 by a press-fit pin 31, and the heat exchange unit 30 is fixed to the second displacer 3 by a press-fit pin 32. Thereby, in both the 1st cooling stage 20 and the 2nd cooling stage 28, the substantial heat exchange area is increased and the cooling efficiency is improved.

  Furthermore, in the regenerator type refrigerator 1 of the first embodiment, as shown in FIG. 1, the high temperature side region 24 inside the second displacer 3 includes a columnar heat transfer member 33 extending in the axial direction. . The heat transfer member 33 is made of a material that can transmit heat larger in the axial direction than at least the regenerator, that is, a material having a large heat conduction coefficient. Specifically, materials having high thermal conductivity such as copper, aluminum, and alloys thereof can be used. The heat transfer member 33 is preferably made of a material having a larger thermal conductivity coefficient than the material constituting the side wall of the regenerator.

  The heat transfer member 33 is embedded in the non-magnetic second regenerator material in the high temperature side region 24, and extends continuously in the axial direction adjacent to the second regenerator material. As is clear from FIG. 1, the high temperature end of the heat transfer member 33 is positioned on the lower temperature side than the lower end of the first cooling stage 20, and the low temperature end of the heat transfer member 33 is higher than the upper end of the second cooling stage 28. Located on the side.

  The position in the axial direction of the heat transfer member 33 in the high temperature side region 24 is determined in consideration of the temperature distribution in the high temperature side region 24 during normal operation of the regenerator refrigerator 1. In a general cryogenic refrigerator, the low temperature end of the lower heat transfer member 33 in FIG. 1 is preferably separated from the partition plate 23 by a predetermined distance to the high temperature side. 1 may be in contact with the rectifier 21. Although not shown in FIG. 1, the heat transfer member 33 may include a support member in order to maintain the axial position in the high temperature side region 24. For example, a cross-shaped support member can be provided at the low temperature end of the heat transfer member 33.

  The region in the axial direction where the low temperature end is located is a region where the specific heat of the helium gas of the refrigerant exceeds the specific heat of the second regenerator material of the nonmagnetic material, and a temperature range of, for example, 8 to 20 K during operation of the refrigerator. This is a region that falls within (more preferably, 8 to 10 K). Further, examples of the cold storage material having a high specific heat in this temperature range include lead and bismuth which are nonmagnetic materials.

  Next, the operation of the refrigerator 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 slightly deviated, high-pressure helium gas is supplied from the supply / discharge common pipe into the first cylinder 7 via the supply valve 15, and is supplied to the upper portion of the first displacer 2. It flows into the 1st regenerator 9 inside the 1st displacer 2 from the 1st opening 13 located. The high-pressure helium gas that has flowed into the first regenerator 9 is supplied to the first expansion space 18 through the second opening 19 and the first clearance that are positioned below the first displacer 2 while being cooled by the first regenerator material. Is done.

  The high-pressure helium gas supplied to the first expansion space 18 flows into the second regenerators 24 and 25 inside the second displacer 3 through the communication passage around the connector 5. The high-pressure helium gas that has flowed into the second regenerators 24 and 25 is cooled by the second regenerator material, and passes through the third opening 27 and the second clearance located at the lower part of the second displacer 3, and thereby the second expansion space 26. To be supplied.

  In this way, the first expansion space 18 and the second expansion space 26 are filled with 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. The helium gas in the first expansion space 18 that has become low temperature due to expansion absorbs heat from the first cooling stage 20 through the first clearance, and the helium gas in the second expansion space 26 cools through the second clearance. Absorbs heat from the stage 28.

  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, the third opening 27, the second regenerators 25 and 24, 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. At that time, the first regenerator material and the second regenerator material are cooled by the refrigerant gas. This process is defined as one cycle, and the refrigerator cools the first cooling stage 20 and the second cooling stage 28 by repeating this cooling cycle.

  According to the regenerator type refrigerator 1 and the second regenerators 24 and 25 of the first embodiment, the following operational effects are obtained. The temperature profile from the high temperature end to the low temperature end of the high temperature side region 24 tends to be inversely proportional to the distance from the high temperature end, and becomes a hyperbolic profile. The intermediate region (8K to 30K) of this temperature profile is shifted to a higher temperature side than the temperature profile when there is no heat transfer member 33 because heat is transferred from the high temperature end by the heat transfer member 33. The rise in the temperature profile inside the high temperature side region 24 reduces the amount of helium gas that accumulates in this region and increases the pressure difference of the entire refrigerator system, so that the refrigeration performance can be improved.

  In addition, since the heat transfer member 33 extends in the axial direction of the second regenerators 24 and 25 and transfers heat from the high temperature end toward the low temperature end, the temperature of the first cooling stage 20 is reduced. Thus, the refrigeration performance of the first cooling stage 20 can be enhanced. Further, since the low temperature end of the heat transfer member 33 is located in a temperature region in which the specific heat of the refrigerant exceeds the specific heat of the cold storage material, even if heat is transferred from the high temperature end of the heat transfer member 33 to the low temperature end, The temperature of the second regenerator material and the refrigerant in the high temperature side region 24 of the second regenerators 24 and 25 near the low temperature end of the heat transfer member 33 is not increased. That is, the refrigeration performance of the first cooling stage 20 can be enhanced while ensuring the refrigeration performance of the second cooling stage 28.

  In addition, although the heat transfer member 33 in FIG. 1 described above is illustratively a cylindrical member, it is easy to manufacture and how to offset the temperature profile, that is, the degree of heat exchange with the second regenerator material or the refrigerant gas. Depending on the situation, it can be appropriately changed. That is, the shape of the cross section perpendicular to the axial direction of the heat transfer member 33 is a circle as shown in FIG. 2 (a), a cylinder as shown in FIG. 2 (b), and an outer peripheral surface as shown in FIG. 3 (c). A circle having a fin shape may be used, and a cross-sectional shape including the axial direction may be a trapezoidal shape having a wide high temperature end as shown in FIG.

  1 is arranged in the center of the high temperature side region 24 of the second regenerators 24, 25. However, as shown in FIG. 3, a plurality of heat transfer members 33 are arranged in the radial direction from the center. It can also be discretely arranged at spaced apart positions. In this case, in consideration of the balance between the total heat capacity of the plurality of heat transfer members 34 and the volume and heat capacity occupied by the second regenerator material, the cross-sectional area per heat transfer member 33 shown in FIG. It can be set as small as appropriate.

  Furthermore, the arrangement form of the heat transfer member is not limited to the above-described form. For example, as shown in FIG. 4, the heat transfer member 35 is formed as a pair of upper and lower disks along the columnar shape of the high temperature side region 24 of the second regenerators 24 and 25. It can also be arranged discretely in the axial direction. Similarly, as shown in FIG. 5, the heat transfer member 36 may be arranged discretely in the axial direction and the radial direction as having a plurality of spherical shapes having a diameter larger than that of the second regenerator material.

  In Example 1 mentioned above and the related modification, although the heat-transfer member shall be arrange | positioned inside a cool storage, it can also be set as the cylindrical shape which encloses the cool storage material which comprises a cool storage. The second embodiment will be described below.

  The regenerator-type refrigerator 41 of the second embodiment shown in FIG. 6 is substantially the same as the one shown in the first embodiment in terms of functions, operation modes, and basic components as a refrigerator. Are denoted by the same reference numerals, and differences will be mainly described.

  The regenerator type refrigerator 41 of the second embodiment includes a cylindrical heat transfer member 42 that encloses the second regenerator material in the high temperature side region 24. The shape of the outer peripheral surface of the heat transfer member 42 coincides with the shape of the outer peripheral surface of the second displacer 3, the high temperature end of the heat transfer member 42 is connected to the high temperature end of the second displacer 3, and the second displacer 3 is heated. It is connected to the pin 6 via the member 42. As described above, the high temperature end of the heat transfer member 42 may be disposed in the first expansion space 18 so as to be located on the higher temperature side than the lower end of the first cooling stage 20 and on the lower temperature side than the upper end in the axial direction. The low temperature end of the heat transfer member 42 is disposed at an axial position that forms a temperature region of 8K to 20K, for example, as described in the first embodiment.

  According to the second embodiment, in the axial arrangement of the heat transfer member 42, the high temperature end can be arranged on the higher temperature side in the axial direction. Thereby, the temperature of the 1st cooling stage 20 can be reduced more effectively.

  In consideration of the fact that the flow velocity tends to decrease as the refrigerant gas flowing through the high temperature side region 24 is separated from the center in the radial direction, for example, as shown in FIG. A disc-shaped heat exchanger 43 having a plurality of flow holes can be appropriately added to the peripheral side. Thereby, the temperature of the 1st cooling stage 20 can be reduced more effectively and refrigeration efficiency can be improved.

  In the second embodiment, the embodiment in which the heat transfer member 42 forms the second displacer side wall has been described as an example. However, the heat transfer member 42 is formed inside the displacer side wall so as to enclose the second cool storage material. May be. Moreover, it is not always necessary to enclose all the second regenerator materials, and the heat transfer member 42 only needs to enclose at least a part of the second regenerator materials.

  In Embodiments 1 and 2 described above, the application form to the two-stage refrigerator of the present invention is shown, but it is of course possible to apply to a single-stage refrigerator. The third embodiment will be described below. In FIG. 8, the same components as those used in the first stage of FIG. 1 are denoted by the same reference numerals, and differences will be mainly described in the following description.

  In the regenerator type refrigerator 51 of the third embodiment, as shown in FIG. 8, a high temperature side region 9 composed of a metal mesh of copper or aluminum is disposed on the upper stage inside the displacer 2, and the high temperature is obtained in the axial direction. A cold storage material different from the high temperature region, for example, a spherical non-magnetic material such as lead or bismuth, is disposed as a cold storage material in the low temperature region 53 positioned on the low temperature side with the partition plate 52 interposed therebetween. . Another partition plate 52 is disposed between the rectifier 11 and the low temperature side end portion of the low temperature side region 53.

  A columnar heat transfer member 54 that extends in the axial direction and is located at the center is disposed inside the low temperature side region 53 in which a plurality of spherical regenerator materials exist. In the third embodiment, the high temperature end of the heat transfer member 54 is separated from the upper partition plate 52, and the low temperature end is also separated from the lower partition plate 52. Also in the third embodiment, the low temperature end of the heat transfer member 54 is disposed at an axial position corresponding to the temperature region of 8K to 20K described in the first and second embodiments.

  According to the regenerator type refrigerator 51 and the regenerators 9 and 53 of the third embodiment, heat is transferred from the high temperature end to the low temperature end of the heat transfer member 54, and the heat transfer member 54 is positioned on the high temperature side. The cold storage material inside the low temperature side region 53 to be cooled is cooled, and the refrigeration capacity of the entire refrigerator can be increased. At the same time, since the low temperature end of the heat transfer member 54 is located in the above-described temperature range, even if heat is transmitted from the high temperature end of the heat transfer member 54, the specific heat of the refrigerant gas exceeds the specific heat of the regenerator material. Therefore, the temperature rise is prevented and it is possible to prevent the refrigeration capacity from being lowered.

  In Embodiments 1 to 3 described above, the present invention is applied to a displacer type refrigerator, but the present invention can also be applied to a pulse tube type refrigerator. Hereinafter, Example 4 will be described.

  As shown in FIG. 9, the pulse tube type regenerator refrigerator 101 of the fourth embodiment includes a first stage regenerator 102, a second stage regenerator 103, a first stage pulse tube 104, and a second stage pulse. And a tube 105. The high temperature ends of the first-stage regenerator 102, the first-stage pulse tube 104, and the second-stage pulse tube 105 are divided into a branch pipe 108 that branches from the discharge side of the compressor 107 and a branch pipe 109 that branches from the suction side, respectively. They are connected via common supply / exhaust pipes 110, 111, 112 corresponding to the high temperature ends.

  A regenerator supply valve V1 is arranged in front of the first connection point P1 to the supply / discharge common pipe 110 of the branch pipe 108, and one stage is in front of the second connection point P2 to the supply / discharge common pipe 111 of the branch pipe 108. The second supply valve V3 is disposed in front of the third connection point P3 of the branch pipe 108 to the supply / discharge common pipe 112.

  A regenerator return valve V2 is disposed in front of the first connection point P1 of the branch pipe 109 to the supply / discharge common pipe 110, and one stage is provided in front of the second connection point P2 of the branch pipe 109 to the supply / discharge common pipe 111. The second return valve V6 is disposed in front of the third connection point P3 of the branch pipe 109 to the supply / discharge common pipe 112.

  A flow rate control valve V7 is disposed between the high temperature end of the first stage pulse tube 104 of the supply / exhaust common pipe 111 and the second connection point P2, and the high temperature end of the second stage pulse pipe 105 of the supply / exhaust common pipe 112 and the second connection point P2. A flow control valve V8 is arranged between the three connection points P3. These flow control valves act as a phase adjustment mechanism for the gas piston generated in the pulse tube. An orifice can be used instead of the flow control valve.

  A rectifying heat exchanger 113 is disposed at the high temperature end of the first-stage pulse tube 104, and a rectifying heat exchanger 114 is disposed at the low temperature end. A rectifying heat exchanger 115 is disposed at the high temperature end of the second-stage pulse tube 105, and a rectifying heat exchanger 116 is disposed at the low temperature end.

  The low-temperature end of the first-stage pulse tube 104 and the low-temperature end of the first-stage regenerator 102 are thermally connected by the first-stage cooling stage 117, and the first-stage low-temperature end connection pipe 118 positioned inside the first-stage cooling stage 117 The low-temperature end of the pulse tube 104 and the low-temperature end of the first stage regenerator 102 are connected so that the refrigerant gas can flow therethrough. The low-temperature end of the second-stage pulse tube 105 and the low-temperature end of the second-stage regenerator 103 are connected by a second-stage low-temperature end connection pipe 119 so that refrigerant gas can flow therethrough.

  Further, in the regenerator type refrigerator 101 of the fourth embodiment, although not shown in FIG. 9, the inside of the second-stage regenerator 103 is similar to the second regenerator of the first embodiment in the upper stage with a nonmagnetic material. A high temperature side region including a low temperature side region having a magnetic regenerator in the lower stage, and extending in the axial direction inside the high temperature side region, for example, a circle having a high thermal conductivity such as copper, aluminum, etc. A columnar heat transfer member 120 is included.

  The heat transfer member 120 is embedded in a spherical nonmagnetic material cold storage material in the high temperature side region, and extends continuously in the axial direction adjacent to the cold storage material. Further, the high temperature end of the heat transfer member 120 is located on the lower temperature side than the lower end of the first stage cooling stage 117, and the low temperature end of the heat transfer member 120 is located on the low temperature end of the second regenerator 103. It is located on the higher temperature side than the upper end.

  The axial region where the low temperature end of the heat transfer member 120 is located is a region in which the specific heat of the helium gas of the refrigerant exceeds the specific heat of the non-magnetic regenerator material, and is, for example, 8-20K during the operation of the refrigerator. This is a region that falls within the temperature range (more preferably, 8 to 10 K).

  In the valve pulse tube type regenerator refrigerator 101 configured as described above, when the first-stage supply valve V3 and the second-stage supply valve V5 are opened in the supply process of the high-pressure refrigerant gas, the refrigerant gas is branched. It flows into the low temperature ends of the first-stage pulse tube 104 and the second-stage pulse tube 105 via the pipe 108 and the supply / discharge common pipe 111 or the supply / discharge common pipe 112.

  When the regenerator supply valve V1 is opened, the refrigerant gas flows from the compressor 107 through the branch pipe 108 and the supply / discharge common pipe 110 and flows from the first stage regenerator 102 to the low temperature end of the first stage pulse pipe 104. Then, it flows into the high temperature end of the second stage pulse tube 105 through the second stage regenerator 103.

  On the other hand, in the process of recovering the low-pressure refrigerant gas, when the first-stage return valve V4 or the second-stage return valve V6 is opened, the refrigerant gas in the first-stage pulse tube 104 or the second-stage pulse tube 105 becomes the high-temperature end. Then, it passes through the supply / discharge common pipe 111 or the supply / discharge common pipe 112 and the branch pipe 109 and is collected by the compressor 107. When the regenerator return valve V2 is opened, the refrigerant gas in the first-stage pulse tube 104 is recovered from the low temperature end to the compressor 107 via the first-stage regenerator 102, the supply / discharge common pipe 110, and the branch pipe 109. Is done. Similarly, the refrigerant gas in the second-stage pulse tube 105 is recovered by the compressor 107 via the second-stage regenerator 103, the first-stage regenerator 102, the supply / discharge common pipe 110, and the branch pipe 109.

  In the pulse tube type regenerator refrigerator 101 of the fourth embodiment, refrigerant gas (for example, helium gas), which is a working fluid compressed by the compressor 107, is used in the first stage regenerator 102, the second stage regenerator 103, and The operation of flowing into the first-stage pulse tube 104 and the second-stage pulse tube 105, and the working fluid are discharged from the first-stage pulse tube 104, the second-stage pulse tube 105, the first-stage regenerator 102, and the second-stage regenerator 103, By repeating the operation collected by the compressor 107, cold is formed at the cold ends of the regenerator and the pulse tube. Moreover, heat can be taken from the object to be cooled by bringing the object to be cooled into thermal contact with these low temperature ends.

  According to the regenerator refrigerator 102 and the upper regenerator of the fourth embodiment, the following operational effects can be obtained. That is, as described in Example 1, the intermediate region of the temperature profile from the high temperature end to the low temperature end of the upper regenerator shifts to the high temperature side, thereby reducing the amount of helium gas accumulated in this region, Since the pressure difference of the entire refrigerator system becomes large, the refrigeration performance can be improved.

  Further, since the heat transfer member 120 extends in the axial direction and transfers heat from the high temperature end to the low temperature end of the heat transfer member 120, the temperature of the first cooling stage 117 is lowered to reduce the first stage refrigeration. Performance can be increased. Since the low temperature end of the heat transfer member 120 is located in a temperature region in which the specific heat of the refrigerant exceeds the specific heat of the regenerator, the heat transfer member 120 can transfer heat from the high temperature end to the low temperature end. The temperature of the regenerator material or refrigerant in the upper regenerator in the vicinity is not increased. That is, the first-stage refrigeration performance can be enhanced after securing the second-stage refrigeration performance.

  Although Example 4 demonstrated the example in which a heat-transfer member is located in the inside of a regenerator, it can also be set as the form which a heat-transfer member encloses a stored material similarly to Example 2. FIG. In addition, although a two-stage pulse tube refrigerator has been described as an example, a single-stage pulse tube can be used as in the third embodiment.

  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.

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

  In the present invention, the efficiency of refrigeration can be increased by installing a heat transfer member extending in the axial direction. Therefore, it can be applied to various regenerator refrigerators and regenerators.

DESCRIPTION OF SYMBOLS 1 Regenerator type refrigerator 2 First displacer 3 Second displacer 4 Pin 5 Connector 6 Pin 7 First cylinder 8 Second cylinder 9 First regenerator 10 Rectifier 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 Rectifier 22 Rectifier 23 Partition plate 24 High temperature side region: 24 + 25: Second regenerator (regenerator of the present invention)
25 Low temperature side region 26 Second expansion space 27 Third opening 28 Second cooling stage 29 Heat exchange section 30 Heat exchange section 31 Press-fit pin 32 Press-fit pin 33 Heat transfer member

Claims (9)

  A regenerator-type refrigerator comprising a regenerator that includes a regenerator and extends in the axial direction, and a heat transfer member that extends adjacent to the regenerator and extends in the axial direction.   The regenerator-type refrigerator according to claim 1, wherein the heat transfer member is located inside the regenerator.   The regenerator-type refrigerator according to claim 2, wherein the heat transfer member is continuously arranged in the axial direction.   The regenerator-type refrigerator according to claim 2, wherein the heat transfer members are discretely arranged in the axial direction.   The regenerator type refrigerator according to claim 1, wherein the heat transfer member is configured to enclose the regenerator material.   The regenerator according to claim 1, wherein the regenerator includes a plurality of cooling stages, and the heat transfer member is disposed between two cooling stages of the plurality of cooling stages. Type refrigerator.   The regenerator-type refrigerator according to any one of claims 1 to 6, wherein the low-temperature end of the heat transfer member is located in a region where the specific heat of the refrigerant exceeds the specific heat of the regenerator material.   The regenerator has a high temperature side region including a cold storage material made of a non-magnetic material and a low temperature side region including a cold storage material made of a magnetic material, and the heat transfer member is disposed in the high temperature side region. The regenerator type refrigerator as claimed in any one of claims 1 to 7.   A regenerator that includes a heat transfer member that includes a heat storage material and extends in the axial direction and extends in the axial direction adjacent to the cold storage material.

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