JP2008292084A - Stirling refrigerating machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a high-performance Stirling refrigerating machine reduced in heat exchange loss while suppressing the drift of an operating fluid. <P>SOLUTION: The Stirling refrigerating machine comprises a case 120 having a sealed end 1201 at least at one end, a seal mechanism 15 stored in the case 120 to form an internal space 101 between the sealed end 1201 and itself where the operating fluid is filled, an expansion space E and a compression space C formed in the internal space 101, a compressor 3 located outside the case 120 to generate a pressure fluctuation in the operating fluid, and heat exchanging means 11, 13 and 14 provided between the expansion space E and the compression space C for heat exchange by the reciprocation of the operating fluid. The seal mechanism 15 has an operating fluid introduction part 1204 for introducing the operating fluid flowing from the compressor 3 into the seal mechanism 15, and a flow equalization promoting means 150 for promoting the equalization of the operating fluid introduced from the operating fluid introduction part 1204 and parting the operating fluid into the heat exchanging means 11, 13 and 14. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a Stirling refrigerating engine using a gas cycle of a working fluid.

  Stirling refrigerators (gas cycle engine refrigerators) are attracting attention as a means for generating low temperatures because they can generate cryogenic temperatures using the gas cycle of the working fluid. Hereinafter, it may be called a simple refrigerator.

  In a conventional Stirling refrigerator (see, for example, Patent Document 1), as shown in FIG. 10, the refrigeration unit 1A and the pressure vibration unit 31x are formed coaxially and integrally. Specifically, in the Stirling refrigerator of Patent Document 1, the refrigeration unit 1A and the pressure vibration unit 31x are coaxially arranged in the case unit 120x. The cylinder (inner cylinder) 11x is inserted into the case portion 120x (outer cylinder). A displacer 13x is disposed inside the cylinder 11x. Further, between the cylinder 11x and the case portion 120x, a heat exchanging portion 14x including a heat absorber 141x, a regenerator 142x, and a radiator 143x is disposed. An expansion chamber E is formed between the tip portion 1201x of the case portion 120x and the heat exchange portion 14x. A compression chamber C is formed between the pressure vibration unit 31x and the heat exchange unit 14x. Further, a communication hole 1500x is formed in the cylinder 11x, the inside and outside of the cylinder 11x are communicated, and a path from the expansion chamber E to the compression chamber C is formed. The working fluid reciprocates between the expansion chamber E and the compression chamber C by the pressure vibration part 31x to exchange heat.

  There is also a Stirling refrigerator (see, for example, Patent Document 2 and Patent Document 3) in which the refrigeration unit 1A and the pressure vibration unit 31x are not integrated but configured as a separate type. As shown in FIG. 11, in the refrigerator of Patent Document 2, a connecting passage 2x is installed between the refrigeration unit 1A and the compressor 3x (pressure vibration unit 31x), and between the refrigeration unit 1A and the compressor 3x. The working fluid flows. A displacer 13x is placed inside the cylinder 11x, and a heat exchanging portion 14x is placed inside the displacer 13x. An expansion chamber E and a compression chamber C are formed in the cylinder 11x through the displacer 13x. Further, the heat exchanging portion 14x communicates with the expansion chamber E and the compression chamber C through a communication hole 1500x formed in the displacer 11x, and a path from the expansion chamber E to the compression chamber C is formed. The working fluid reciprocates between the expansion chamber E and the compression chamber C by the compressor 3x to exchange heat.

As shown in FIG. 12, in the refrigerator of Patent Document 3, as in Patent Document 1, the heat exchanging portion 14x is disposed between the cylinder (inner cylinder) 11x and the case portion 120x (outer cylinder). However, the refrigeration unit 1A and the compressor 3x are of the separated type communicated via the connection passage 2x. Furthermore, as an improved version of the refrigerator disclosed in Patent Document 3, as shown in FIG. 13, a compression space C is formed, and the working fluid introduced from the compressor 3x flows through the compression space C to the heat exchange unit 14x. It is like that.
Japanese Patent Laid-Open No. 2001-355513 (pages 1 to 5, FIG. 1) Japanese Examined Patent Publication No. 6-82020 (Pages 1-5, Fig. 1) JP 2000-292022 A (pages 1-7, FIG. 4)

  Since the refrigerator of Patent Document 1 is a coaxial integrated type, when the refrigerator is attached (arranged) to another device (for example, a low-temperature storage device such as a refrigerator), it can be freely attached depending on the length of the refrigerator in the long axis direction. The degree is limited, and it is difficult to make the entire apparatus compact.

  Moreover, in the refrigerator of patent document 2, although it became easy to attain the compactness of the apparatus by adopting the separation type, the regenerator material (member in the regenerator) mainly constituting the heat exchanging unit 14x is mainly the displacer 13x. The displacer 13x is heavy (mass). Thereby, the refrigerator of patent document 2 is difficult to operate in a high frequency band.

  Moreover, in the refrigerator of patent document 3, the weight of the displacer 13x is aimed at by installing the cool storage material of the heat exchange part 14x between the cylinder (inner cylinder) 11x and the case part 120x (outer cylinder). However, as shown in FIG. 12, the connecting passage 2x is connected to the cylinder 11x so as to open to one side 14a of the heat exchanging portion 14x (cold storage material). For this reason, the working fluid is liable to drift, and an area (dead space) in which the working fluid hardly flows is likely to be generated on the other side 14b of the heat exchanging portion 14x (cold storage material). That is, it becomes difficult for the working fluid to uniformly flow through the heat exchanging portion 14x, so that heat exchange loss occurs and heat exchange cannot be performed efficiently. Therefore, it is difficult to improve the efficiency of the entire apparatus of the refrigerator.

  Furthermore, in the refrigerator that is an improved type of the refrigerator of Patent Document 3, when the working fluid flows from the side wall of the cylinder 11x to the compression space C via the connection passage 2x, the working fluid is opened on the opening side of the connection passage 2x ( There is a tendency to flow easily from one side 14a) to the back side (the other side 14b) of the compression space C. As a result, the working fluid easily flows to the other side 14b of the heat exchanging portion 14x. For this reason, the working fluid is liable to drift, and a region (dead space) where the working fluid hardly flows is likely to be generated on one side 14a of the heat exchanging portion 14x (cool storage material), thereby improving the efficiency of the entire apparatus. Is difficult. In addition, FIG. 14 shows the II-II cross section of the refrigerator shown in FIG.

  This invention is made | formed in view of the said actual condition, and makes it a subject to provide the high performance Stirling refrigerator which can suppress the drift of a working fluid and has few heat exchange losses.

The Stirling refrigerator of the present invention has a case portion provided with a sealed end at least at one end;
A seal mechanism that forms an internal space that is accommodated in the case portion and encloses the working fluid between the sealed end, an expansion space that is installed in the internal space and expands the working fluid, and a compression space that compresses the working fluid A compressor that is located outside the case portion and generates pressure fluctuations with respect to the working fluid, and heat exchange means that exchanges heat by reciprocating the working fluid between the expansion space and the compression space. And a sealing mechanism that promotes equalization of the working fluid introduced from the working fluid introduction portion and introduces the working fluid introduced from the compressor into the sealing mechanism, and distributes the fluid to the heat exchange means. And a flow promoting means.

  According to the Stirling refrigerator of the present invention, an expansion space and a compression space are formed in the internal space of the case portion, and are positioned outside the expansion space, the compression space, and the case portion, and generate pressure fluctuations with respect to the working fluid. Heat exchange can be performed based on the working fluid reciprocating between the compressor and the compressor. Further, in the Stirling refrigerator of the present invention, since the compressor is positioned outside the case portion, the compressor and the case portion can be arranged separately. Thereby, size reduction of a case part can be implement | achieved and a case part and a compressor can be arrange | positioned as freely as possible, respectively. That is, the degree of freedom in mounting (arrangement) between the case portion and the compressor is improved, and the entire apparatus can be easily made compact. Furthermore, since the sealing mechanism of the Stirling refrigerator of the present invention has equalization promoting means for promoting equalization of the working fluid flowing in from the compressor via the working fluid introduction part and diverting it to the heat exchange means, The uneven flow of the working fluid in the exchange means is suppressed, and the working fluid can flow through the heat exchange means as evenly as possible. Thereby, the heat exchange loss which generate | occur | produces by the drift of the working fluid in a heat exchange means decreases, and the efficiency of a heat exchange means can be improved. As a result, the efficiency of the entire apparatus is improved, and a high-performance Stirling refrigerator can be realized.

  The heat exchanging means of the Stirling refrigerator of the present invention is accommodated between the cylinder and the case part, the cylinder accommodated in the internal space, arranged coaxially with the case part, the displacer slidably contacted with the cylinder, and the cylinder and the case part. A heat exchanging unit comprising a heat exchanger and a regenerator, the expansion space is formed between the sealed end and the heat exchanging unit, and the compression space is formed of the heat exchanging unit, the seal mechanism, and the case unit. It is preferable that it is formed between the compressor and the compressor which is located outside the cylinder and generates pressure fluctuation with respect to the working gas. By providing a cylinder arranged coaxially with the case part, a heat exchange part can be installed between the case part and the cylinder. For this reason, the weight of the displacer placed in sliding contact with the cylinder can be reduced. That is, it is not necessary to install a heat exchange part in the displacer, and the weight of the displacer is reduced. Therefore, the refrigerator can be operated in a high frequency range (compression-expansion cycle), which is advantageous for improving the refrigeration performance of the Stirling refrigerator.

  It is preferable that a connecting passage for communicating between the compressor of the Stirling refrigerator of the present invention and the working fluid introducing portion is provided. Thereby, the Stirling refrigerator of this invention can attach a heat exchange means and a compressor separately, and the freedom degree of arrangement | positioning of an apparatus improves. Therefore, the separation type Stirling refrigerator can be made compact.

  The flow equalization promoting means of the Stirling refrigerator of the present invention is formed in the seal mechanism, formed in the center opening passage that opens in the center of the compression space along the longitudinal direction of the case portion, and in the seal mechanism, and the working fluid introduction A circumferential flow passage that causes the working fluid flowing in from the compressor through the section to flow along the circumferential direction of the seal mechanism, and a radial direction of the seal mechanism that is formed along the radial direction, and one end communicates with the circumferential flow passage. And a plurality of dispersion passages whose other ends communicate with the central opening passage, and the working fluid that has flowed into the seal mechanism from the compressor passes through the circumferential flow passage, the plurality of dispersion passages, and the central opening passage, It is preferable that they are gathered at the center of the compression space and flow from the center to the heat exchange section.

  Thereby, the working fluid flowing from the compressor to the seal mechanism can flow as evenly as possible in the entire circumferential direction of the seal mechanism along the circumferential flow passage of the seal mechanism. Further, the working fluid is collected from the circumferential flow passage to the central opening passage through the plurality of dispersion passages. Further, the working fluid can flow into the central portion of the compression space through the central opening passage. The working fluid flowing into the central portion can flow so as to be dispersed as evenly as possible in the heat exchange portion sandwiched between the case portion and the cylinder. Therefore, the flow equalization promoting means of the Stirling refrigerator of the present invention can distribute and flow the working fluid to the heat exchange part as evenly as possible. Thereby, heat exchange is promoted as uniformly as possible, and the efficiency of the heat exchange means can be improved.

  The plurality of dispersion passages of the Stirling refrigerator of the present invention are preferably formed in the sealing mechanism symmetrically and equidistantly with the long axis of the case part as the axis of symmetry.

  By forming the dispersion passage symmetrically and equidistantly in the sealing mechanism, the working fluid that has flowed through the circumferential flow passage formed in the sealing mechanism is distributed and guided to the plurality of dispersion passages, and is heated as evenly as possible. Distributed to the exchange. Further, since the plurality of dispersion passages are arranged symmetrically and equidistantly, the pressure of the working fluid in the circumferential flow passage of the seal mechanism can be made as uniform as possible.

  The sealing mechanism of the Stirling refrigerator of the present invention includes an opposing end portion facing the compression space, and the opposing end portion is an inclined surface that rises along the direction from the center toward the outer periphery with the long axis of the case portion as the center. It is preferable to provide.

  By providing an inclined surface that rises along the direction from the center toward the outer periphery at the opposite end of the seal mechanism, the working fluid collected in the central opening passage can be more easily distributed along the inclined surface as evenly as possible. And it can flow to a heat exchange part so that it may spread. That is, the working fluid discharged from the center is guided to the inclined surface. The working fluid can flow in the dispersion direction so as to rise about the center. Therefore, the working fluid can be fed into the heat exchange part as evenly as possible. Thereby, heat exchange is promoted as uniformly as possible, and the efficiency of the heat exchange means can be improved.

  The flow equalization promoting means of the Stirling refrigerator of the present invention is formed in the seal mechanism, and a circumferential flow passage that allows the working fluid flowing from the compressor through the working fluid introduction portion to flow along the circumferential direction of the seal mechanism. A plurality of dispersed opening passages formed along the major axis direction of the seal mechanism, one end communicating with the circumferential flow passage, the other end communicating with the compression space, and opening facing the heat exchange unit; The working fluid that has flowed into the case portion from the compressor preferably flows to the heat exchange portion via the circumferential flow passage and the plurality of dispersion opening passages.

  According to the Stirling refrigerator of the present invention, the flow equalization promoting means communicates with the circumferential flow passage that flows in the circumferential direction of the seal mechanism and the plurality of dispersions that open to face the heat exchange portion. By providing the opening passage, the working fluid flowing from the working fluid introduction portion to the seal mechanism can flow as evenly as possible in the entire circumferential direction of the seal mechanism along the circumferential flow passage of the seal mechanism. In addition, the working fluid can be discharged from the circumferential flow passage so as to face the heat exchange portion via the plurality of dispersion opening passages. That is, the working fluid flowing in the circumferential direction of the seal mechanism can be distributed and flowed as evenly as possible to the heat exchange section through the plurality of dispersed opening passages. Thereby, heat exchange is promoted as uniformly as possible, and the efficiency of the heat exchange means can be improved.

  The plurality of dispersed opening passages of the Stirling refrigerator of the present invention are preferably formed in the seal mechanism symmetrically and equidistantly with the long axis of the case portion as the axis of symmetry.

  By forming the dispersion opening passages symmetrically and equidistantly in the sealing mechanism, the working fluid that has flowed through the circumferential flow passage formed in the sealing mechanism is distributed and guided to the flow paths of the plurality of dispersion opening passages. , Distributed as evenly as possible to the heat exchanger. Further, since the plurality of dispersed opening passages are arranged symmetrically and equidistantly, the pressure of the working fluid in the circumferential flow passage of the seal mechanism can be made as uniform as possible.

  It is preferable that the uniform flow promoting means of the Stirling refrigerator of the present invention includes a rectifying unit that rectifies the flow of the working fluid between the heat exchange unit and the seal mechanism. By providing the rectifying unit between the sealing mechanism and the heat exchange unit, the working fluid can flow to the heat exchange unit as evenly as possible. That is, the working fluid flowing into the compression space through the plurality of dispersion opening passages is further promoted by the rectification unit, and can flow into the heat exchange unit as evenly as possible. Therefore, the working fluid can flow through almost the entire heat exchanging portion, heat exchange is promoted as uniformly as possible, and the efficiency of the heat exchanging means can be improved. This is advantageous for improving the efficiency of the entire apparatus including the heat exchange section.

  The heat exchange means of the Stirling refrigerator of the present invention preferably absorbs heat from the side to be frozen through the sealed end. Moreover, it is preferable that the to-be-frozen side of the Stirling refrigerator of this invention is a refrigerator provided with a freezing room, and the sealed end part is installed in the freezing room of the refrigerator. Thereby, the Stirling refrigerator of this invention can absorb heat from the to-be-frozen side via the closed end part of a case part. Moreover, when the to-be-frozen side is comprised from a refrigerator, a freezer compartment can be cooled by inserting the sealing end part of the case part of the Stirling refrigerator of this invention in the freezer compartment of a refrigerator. In the Stirling refrigerator of the present invention, since the compressor is located outside the case portion, the case portion side and the compressor side are connected via a connecting passage. Thereby, the compressor can be separated from the case portion in which the heat exchange means is accommodated, the degree of freedom in arranging the refrigerator is improved, and the compactness can be achieved. Therefore, the Stirling refrigerator can be easily assembled in the refrigerator, and the Stirling refrigerator can be used as a refrigerator for the refrigerator.

  According to the Stirling refrigerator of the present invention, an expansion space and a compression space are formed in the internal space of the case portion, and are positioned outside the expansion space, the compression space, and the case portion, and generate pressure fluctuations with respect to the working fluid. Heat exchange can be performed based on the working fluid reciprocating between the compressor and the compressor. Further, in the Stirling refrigerator of the present invention, since the compressor is positioned outside the case portion, the compressor and the case portion can be arranged separately. Thereby, size reduction of a case part can be implement | achieved and a case part and a compressor can be arrange | positioned as freely as possible, respectively. That is, the degree of freedom in mounting (arrangement) between the case portion and the compressor is improved, and the entire apparatus can be easily made compact. Furthermore, since the sealing mechanism of the Stirling refrigerator of the present invention has equalization promoting means for promoting equalization of the working fluid flowing in from the compressor via the working fluid introduction part and diverting it to the heat exchange means, The uneven flow of the working fluid in the exchange means is suppressed, and the working fluid can flow through the heat exchange means as evenly as possible. Thereby, the heat exchange loss which generate | occur | produces by the drift of the working fluid in a heat exchange means decreases, and the efficiency of a heat exchange means can be improved. As a result, the efficiency of the entire apparatus is improved, and a high-performance Stirling refrigerator can be realized.

  The Stirling refrigerator of the present invention will be described with reference to the drawings.

(First embodiment)
As shown in FIG. 1, the Stirling refrigerator 100 of the present embodiment (hereinafter may be simply referred to as a refrigerator 100) is used by being attached to a kitchen refrigerator 900 for home use or business use. It is. FIG. 1 is a side view of the refrigerator 900 in a state where the refrigerator 100 according to this embodiment is attached.

  Specifically, as shown in FIG. 1, a refrigerator 900 according to the present embodiment has a door 910 installed on a front surface 901 and a refrigerator 100 attached to a rear surface 902 thereof.

  The refrigerator 100 is mainly composed of a refrigeration unit 1 and a compressor 3. As shown in FIG. 1, the refrigeration unit 1 is installed inside the case unit 120, and a connection passage 2 (connection pipe) is disposed between the refrigeration unit 1 (case unit 120) and the compressor 3. Has been. That is, the refrigeration unit 1 (case unit 120) is connected to the compressor 3 through the connection passage 2. Further, the compressor 3 is located outside the direction intersecting the major axis Y (shown in FIG. 2) direction of the case portion 120.

  Moreover, as shown in FIG. 1, the freezing part 1 is equipped with the heat absorption part 140 (it is comprised from the sealing end part 1201 of the case part 120) mentioned later. Further, the heat absorption unit 140 is inserted and fixed from the rear surface 902 of the refrigerator 900 into the freezer compartment 920 of the refrigerator 900. That is, the refrigeration unit 1 can absorb the heat in the freezer compartment 920 of the refrigerator 900 through the heat absorption unit 140. The compressor 3 is installed on the ground near the rear surface 902 of the refrigerator 900. In addition, the installation method of the compressor 3 can be freely adjusted according to the installation place of the refrigerator 900, etc. In this way, the arrangement of the refrigeration unit 1 and the compressor 3 can be freely adjusted (separated arrangement), and the refrigerator 100 can be easily downsized. For example, as shown in FIG. 1, the compressor 3 can be arranged separately from the refrigeration unit 1 (case unit 120), so that the depth H 1 of the refrigerator 900 to which the refrigeration unit 1 is attached can be reduced as much as possible. it can. Therefore, it is advantageous to make the refrigerator 900 compact.

  Next, the refrigerator 100 according to the present embodiment will be described.

  FIG. 2 is a conceptual diagram of the refrigerator 100 of the present embodiment. As shown in FIG. 2, the refrigerator 100 of the present embodiment mainly includes a refrigeration unit 1, a compressor 3, and a connecting passage 2.

  The refrigerator 100 includes a cylindrical case portion 120, and the case portion 120 includes a sealed end portion 1201, a bottom portion 1202 (shown in FIG. 5), and a side wall portion 1203.

  A disc-shaped sealing mechanism 15 is installed inside the case portion 120 and fixed to the side wall portion 1203 of the case portion 120. By the sealing mechanism 15, the internal space of the case unit 120 is divided into the refrigeration generating unit 101 and the spring chamber 162. A working fluid is enclosed in the refrigeration generating unit 101. In addition, the freezing generation | occurrence | production part 101 comprises the internal space of the case part 120 of this invention. Moreover, helium, nitrogen, a carbon dioxide etc. can be illustrated as a working fluid used for the Stirling refrigerator 100 of this embodiment example, for example. However, the present invention is not limited to this.

  Further, as shown in FIG. 2 or FIG. 3, a seal ring portion 171 is formed on the outer periphery of the seal mechanism 15, and leakage of the working fluid between the refrigeration generating portion 101 and the spring chamber 162 is suppressed. ing.

  In the refrigeration generating unit 101, a cylindrical cylinder 11 that is coaxial (long axis Y) with the case unit 120 is disposed, and is fixed to the case unit 120 via a fixing unit (not shown). A displacer 13 is slidably contacted with the cylinder 11. The displacer 13 is supported by the rod portion 16. Further, a support opening 155 is formed at the center of the seal mechanism 15 (the axial center of the long axis Y of the case portion 120), and the rod portion 16 is slidably contacted with the support opening 155 and inserted into the spring chamber 162. Has been. Sealing is performed between the support opening 155 and the rod portion 16 to suppress leakage of the working fluid. A spring 161 is installed in the spring chamber 162. One end of the spring 161 is fixed to the bottom portion 1202 (shown in FIG. 5) of the case portion 120, and the other end is fixed to the rod portion 16. Accordingly, the displacer 13 can freely vibrate (reciprocate) in the cylinder 11 along the long axis Y direction of the case portion 120 by the elasticity of the spring 161.

  The heat exchange unit 14 is accommodated between the case unit 120 and the cylinder 11. The heat exchange unit 14 includes a heat absorber 141, a radiator 143, and a regenerator 142. The heat absorber 141 and the radiator 143 constitute the heat exchanger of the present invention. The heat absorber 141 absorbs external heat into the working fluid. The heat radiator 143 releases heat from the working fluid to the outside.

  The cylinder 11, the displacer 13, and the heat exchanging unit 14 constitute a heat exchanging means for the Stirling refrigerator of the present invention. Further, as shown in FIG. 2, an expansion space E for expanding the working fluid is formed between the heat exchanging portion 14 (heat absorber 141) and the closed end portion 1201 of the case portion 120. A compression space C for compressing the working fluid is formed between the heat exchange unit 14 (heat radiator 143) and the seal mechanism 15. That is, the heat exchange means (the cylinder 11, the displacer 13, and the heat exchange unit 14) partitions the internal space (the refrigeration generating unit 101) of the case unit 120, thereby forming an expansion space E and a compression space C. Further, the heat exchanging means (refrigeration unit 1) can exchange heat based on the working fluid reciprocating between the expansion space E and the compression space C. Note that the Stirling refrigerator 100 of the present embodiment can generate a low temperature of, for example, −50 to −70 ° C. However, the present invention is not limited to this.

  In addition, as shown in FIG. 2, the working fluid flowing from the compressor 3 through the connection passage 2 is applied to a predetermined position (a position where the seal mechanism 15 is fixed inside) of the side wall 1203 of the case 120. A working fluid introduction part 1204 to be introduced into the seal mechanism 15 is formed. Accordingly, the working fluid flowing from the compressor 3 can be introduced into the case portion 120 from the side surface (side wall portion 1203) of the case portion 120. The compressor 3 generates pressure fluctuations in the working fluid sealed in the refrigeration generating unit 101 of the case unit 120.

  Next, the seal mechanism 15 that is a feature of this embodiment will be described.

  As shown in FIG. 3 or FIG. 4, the seal mechanism 15 includes a flow equalization promoting means 150. The uniform flow promoting means 150 promotes equalization of the working fluid introduced from the working fluid introduction unit 1204. FIG. 3 is an enlarged view around the seal mechanism 15 of the refrigerator 100 of the present embodiment shown in FIG. FIG. 4 shows a cross-section at the II position of the seal mechanism shown in FIG.

  Specifically, as shown in FIG. 4, the seal mechanism 15 is formed with a central opening passage 153 that opens to the central portion of the compression space C along the long axis Y direction of the case portion 120. The center opening passage 153 has a diameter larger than the outer diameter of the rod portion 16 passing through the center portion, and is formed as a cylindrical flow path surrounding the outer periphery of the rod portion 16.

  Further, a ring-shaped circumferential flow passage 151 is formed in the seal mechanism 15 on the outer periphery of the seal mechanism 15. In other words, the circumferential flow passage 151 is formed as a ring-shaped groove on the outer peripheral side surface of the seal mechanism 15, and further, the flow path of the working fluid is partitioned together with the case portion 120 covering the ring-shaped groove.

  Furthermore, a plurality of (four) dispersion passages 152 are formed in the sealing mechanism 15 along the radial direction of the sealing mechanism 15, one end communicating with the circumferential flow passage 151 and the other end communicating with the opening passage 153. Is formed. The number of dispersion passages 152 is not limited to four. It is preferable that at least two dispersion passages 152 are formed. By forming the plurality of dispersion passages 152, the working fluid is easily equalized.

  In this way, the flow equalization promoting means 150 is configured by the circumferential flow passage 151, the dispersion passage 152, and the central opening passage 153. As a result, the working fluid that has flowed in from the connection passage 2 flows through the working fluid introduction part 1204 and then flows in a symmetrical manner along the circumferential direction of the seal mechanism 15 (directions D1 and D2 shown in FIG. 4). Then, the working fluid flowing in the circumferential flow passage 151 flows into the central opening passage located in the center via the four dispersion passages 152. The working fluid collected in the central opening passage 153 flows toward the compression space C along the central opening passage 153. As described above, the working fluid is introduced into the seal mechanism 15 via the working fluid introduction unit 1204, and can flow to the center of the compression space C via the flow equalization promoting means 150 of the seal mechanism 15. For this reason, the working fluid can flow as evenly as possible to the heat exchanging portion 14 without drifting from the central portion of the compression space C. In other words, the working fluid can flow as evenly as possible to the heat exchanging portion 14 by the uniform flow promoting action of the uniform flow promoting means 150, and heat can be exchanged efficiently.

  Also, as shown in FIG. 4, the four dispersion passages 152 are formed in the seal mechanism 15 symmetrically and equidistantly with the axis of the major axis Y of the case portion 120 as the axis of symmetry.

  The flow path diameters of the circumferential flow passage 151, the dispersion passage 152, and the central opening passage 153 can be optimized according to the working fluid (flow rate, volume, etc.). Further, the number of dispersion passages 152, the distance between the dispersion passages, and the like can be optimized according to the dimensions of the seal mechanism.

  Moreover, as shown in FIG. 2 or FIG. 3, the seal mechanism 15 of the Stirling refrigerator 100 according to the present embodiment includes an opposing end 154 facing the compression space C. The opposite end 154 includes an inclined surface 1541 that rises along the direction from the center toward the outer periphery, with the axis of the major axis Y of the case portion 120 as the center.

  The displacer 13 includes a first end surface 131 (shown in FIG. 2) and a second end surface 132. The second end surface 132 is formed as an inclined surface that rises along the direction from the long axis Y of the case portion 120 toward the outer periphery. As described above, in the expansion space C, the promotion flow path C <b> 1 is formed between the second end surface 132 and the inclined surface 1541 so that the working fluid easily flows from the central opening passage 153 toward the heat exchange unit 4.

  Next, the operation principle of the Stirling refrigerator 100 of this embodiment will be briefly described. Note that the Stirling refrigerator 100 of the present embodiment has the same refrigeration principle as a general Stirling refrigerator. This will be described with reference to FIG. The pressure is periodically changed by the compressor 3 and the displacer 13, and the working fluid in the refrigeration generating unit 101 is reciprocated (flowed) between the expansion space E and the compression space C.

  Specifically, the working fluid is compressed by the compressor 3 and the compression space C, is radiated by the radiator 143, passes through the heat exchanger 14 in the order of the regenerator 142 and the heat absorber 141, and flows into the expansion space E. The working fluid that has flowed into the expansion space E is expanded to a low temperature. The working fluid that has reached a low temperature again passes through the heat exchanger in the order of the heat absorber 141, the regenerator 142, and the radiator 143, and flows into the compressor 3 and the compression space C. At this time, heat is absorbed from the outside through the sealed end 1201 by the cold heat of the working fluid having a low temperature through the heat absorber 141. In this way, the compression-expansion cycle of the working fluid is repeated. Thereby, it can absorb heat from the to-be-frozen side (refrigerator 900 shown in FIG. 1) via the heat absorber 141 of the case part 120.

  As described above, in the Stirling refrigerator 100 according to the present embodiment, the expansion space E and the compression space C are formed in the internal space (the refrigeration generating unit 101) of the case portion 120, and the space between the expansion space E and the compression space C is formed. Heat exchange can be performed based on the reciprocating working fluid. Further, in the Stirling refrigerator 100 of the present embodiment example, since the compressor 3 is positioned outside in the direction intersecting the long axis Y direction of the case portion 120, the compressor 3 and the case portion 120 are arranged separately. can do. Thereby, size reduction of the case part 120 is realizable, and the case part 120 and the compressor 3 can each be arrange | positioned freely as much as possible. That is, the degree of freedom of attachment (arrangement) between the case portion 120 and the compressor 3 is improved, and the entire apparatus can be easily downsized. Furthermore, the sealing mechanism 15 of the Stirling refrigerator 100 of the present embodiment promotes equalization of the working fluid flowing from the compressor 3 via the working fluid introduction unit 1204, thereby refrigerating unit 1 (heat exchange unit 14). Therefore, the flow of working fluid in the refrigeration unit 1 (heat exchange unit 14) is suppressed, and the working fluid can flow as evenly as possible to the refrigeration unit 1 (heat exchange unit 14). it can. Thereby, the heat exchange loss which generate | occur | produces by the drift of the working fluid in the freezing part 1 (heat exchange part 14) decreases, heat exchange is accelerated | stimulated as uniformly as possible, and the efficiency of the freezing part 1 can be improved. As a result, the efficiency of the entire refrigerator 100 device is improved, and a high-performance Stirling refrigerator can be realized.

  Further, in the Stirling refrigerator 100 of the present embodiment, the heat exchange unit 14 is installed between the case unit 120 and the cylinder 11 by including the cylinder 11 disposed coaxially with the case unit 120 (long axis Y). can do. For this reason, the weight of the displacer 13 placed in sliding contact with the cylinder 11 can be reduced. That is, it is not necessary to install the heat exchanging unit 14 in the displacer 13, and the weight of the displacer 13 is reduced. Therefore, the refrigerator 100 can be operated in a high frequency range (compression-expansion cycle), which is advantageous in improving the refrigeration performance of the Stirling refrigerator 100.

  Moreover, in the Stirling refrigerator 100 of this embodiment, the freezing part 1 and the compressor 3 can be attached separately, and the freedom degree of arrangement | positioning of an apparatus improves. Therefore, the separation type Stirling refrigerator can be made compact.

  Further, in the Stirling refrigerator 100 of the present embodiment example, the working fluid flowing from the compressor 3 to the seal mechanism 15 is as uniform as possible in the entire circumferential direction of the seal mechanism 15 along the circumferential flow passage 151 of the seal mechanism 15. Can flow. Further, the working fluid is collected from the circumferential flow passage 151 to the central opening passage 153 via the plurality of dispersion passages 152. Further, the working fluid can flow into the central portion of the compression space C through the central opening passage 153. The working fluid flowing into the central portion can flow so as to be dispersed as evenly as possible in the heat exchanging portion 14 sandwiched between the case portion 120 and the cylinder 11. Therefore, the uniform flow promoting means 150 of the Stirling refrigerator 100 according to the present embodiment can distribute the working fluid to the heat exchanging unit 14 and flow it as evenly as possible. Thereby, heat exchange is accelerated | stimulated as uniformly as possible, and the efficiency of the freezing part 1 can be improved.

  Further, in the Stirling refrigerator 100 of the present embodiment, the working fluid that has flowed through the circumferential flow passage 151 formed in the seal mechanism 15 by forming the dispersion passage 152 symmetrically and equidistantly in the seal mechanism 15. Are distributed in a plurality of distribution passages 152 and distributed to the heat exchange unit 14 as evenly as possible. Further, since the plurality of dispersion passages 152 are arranged symmetrically and equidistantly, the pressure of the working fluid in the circumferential flow passage 151 of the seal mechanism 15 can be made as uniform as possible.

  Further, in the Stirling refrigerator 100 of the present embodiment example, the opposed end portion 154 of the seal mechanism 15 is gathered in the central opening passage 153 by providing the inclined surface 1541 rising along the direction from the center toward the outer periphery. The working fluid can more easily flow to the heat exchanging portion 14 so as to spread along the inclined surface 1541 (promoting flow path C1) as evenly as possible. That is, the working fluid discharged from the central portion of the central opening passage 153 into the compression space C is guided to the inclined surface 1541. The working fluid can flow in the dispersion direction so as to rise about the central portion of the central opening passage 153. Therefore, the working fluid can be fed into the heat exchange unit 14 as evenly as possible. Thereby, heat exchange is accelerated | stimulated as uniformly as possible, and the efficiency of the freezing part 1 (heat exchange means) can be improved.

  Moreover, the heat absorption which generate | occur | produces in the freezing part 1 of the Stirling refrigerator 100 of this embodiment is output to the to-be-frozen side (refrigerator 900) via the airtight edge part 1201 (heat absorption part 140). Since the sealed end 1201 (the heat absorption unit 140) is installed in the freezer compartment 920 of the refrigerator 900, the freezer compartment 920 can be cooled. That is, as shown in FIG. 5, the heat absorption part 140 (the sealed end part 1201 of the case part 120) of the refrigeration part 1 of the refrigerator 100 is inserted into the freezer compartment 920 from the rear surface 902 of the refrigerator 900 through the heat insulating material 990. Are arranged horizontally. Further, the spring chamber 162 including the bottom portion 1202 of the case portion 120 is disposed so as to protrude from the rear surface 902 of the refrigerator 990 (projection distance H2).

  In addition, the Stirling refrigerator 100 according to the present embodiment is a separation type in which the case portion 120 and the compressor 3 are connected via the connecting passage 2, so the compressor 3 is connected to the case portion 120 via the connecting passage 2. It is connected to the side wall portion 1203 and installed. That is, the compressor 3 is connected to the side wall portion 1203 (shown in FIG. 2) of the case portion 120 in the direction intersecting the long axis Y (shown in FIG. 2) of the case portion 120 (shown in FIG. 2) via the connecting passage 2. ). For this reason, when attached to the refrigerator 900, the protrusion distance H2 (a part of the depth H1 of the refrigerator 900) by which the case portion 120 protrudes from the rear surface 902 of the refrigerator 900 is the conventional integrated refrigerator shown in FIG. Can be reduced as much as possible from the protrusion distance H2. Therefore, it is easy to make the refrigerator 900 including the refrigerator 100 compact. FIG. 5 shows a state in which the case part 120 of the Stirling refrigerator 100 in the first embodiment is attached to the refrigerator 900.

  As shown in FIG. 6, in the conventional integrated refrigerator, the vibration generator 31x functioning as the compressor 3 is arranged in the case part 120x coaxially with the refrigeration part 1A (long axis Y). The protrusion distance H2 that protrudes from the rear surface 902 of the refrigerator 900 of the case portion 120x becomes large, and it is difficult to make the refrigerator 900 including the refrigerator 100x compact. FIG. 6 shows a state where the case portion 120x of the conventional refrigerator 100x is attached to the refrigerator 900.

  In the conventional integrated refrigerator shown in FIG. 6, the vibration generating device 31x is formed integrally with the case portion 120x, and therefore the vibration from the vibration generating device 31x is directly transmitted to the refrigerator 900 through the case portion 120x. Will be conducted. With respect to this problem, in the refrigerator 100 according to the present embodiment, the compressor 3 is connected to the case portion 120, particularly the heat insulating material 990 side of the rear surface 902, via the connecting passage 2, and thus occurs in the compressor 3. The vibration to be reduced is reduced by the connecting passage 2 or the heat insulating material 990 and is not easily conducted to the case portion 120. Thereby, the influence of the vibration from the compressor 3 on the refrigerator 900 can be suppressed.

  As described above, the Stirling refrigerator 100 according to the present embodiment can output the refrigeration power to the refrigerated side (refrigerator 900) through the sealed end 201 (heat absorption part 140) of the case part 120. Moreover, when the to-be-frozen side is comprised from the refrigerator 900, by inserting the sealing end part 1201 (heat absorption part 140) of the case part 120 of the Stirling refrigerator 100 of this embodiment into the freezer compartment 920 of the refrigerator 900. The freezer compartment 920 can be cooled. Further, in the Stirling refrigerator 100 of the present embodiment example, the compressor 3 is positioned outside the case part 120, so the case part 120 (freezing part 1) side and the compressor 3 side are connected to the connecting passage 2. Connected through. That is, the compressor 3 can be separated from the refrigeration unit 1, the degree of freedom of the arrangement of the refrigerator 100 can be improved, the size of the compressor 3 can be reduced, and the influence of vibration from the compressor 3 to the refrigerator 900 can be suppressed. . Therefore, the Stirling refrigerator 100 can be easily assembled in the refrigerator 900, and the Stirling refrigerator 100 can be used as a freezing means of the refrigerator 900.

(Second Embodiment)
This embodiment is basically the same as the configuration of the first embodiment. Hereinafter, a different part from the first embodiment will be described. Note that portions similar to those in the first embodiment are described using the same reference numerals.

  FIG. 7 shows a cross section of the sealing mechanism 15 of the Stirling refrigerator 100 (shown in FIG. 2) of the present embodiment. 7 is a cross-sectional view at the same position as the II cross-sectional position of the seal mechanism 15 of the first embodiment shown in FIG. As shown in FIG. 7, the Stirling refrigerator 100 according to the present embodiment is different from the refrigerator 100 according to the first embodiment with respect to the seal mechanism 15.

  Specifically, as shown in FIG. 7, in the sealing mechanism 15 of the present embodiment, the circumferential flow passage 151 of the flow equalization promoting means 150 is configured by a ring-shaped flow path having a smaller diameter. That is, the circumferential flow passage 151 can reduce the (flow path) volume of the circumferential flow passage 151 by reducing the diameter of the ring-shaped flow passage. Therefore, the dead volume of the working fluid can be reduced, and the efficiency of the refrigerator 100 can be improved.

(Third embodiment)
This embodiment is basically the same as the configuration of the first embodiment. Hereinafter, a different part from the first embodiment will be described. Note that portions similar to those in the first embodiment are described using the same reference numerals.

  FIG. 8 shows the sealing mechanism 15 of the Stirling refrigerator 100 (shown in FIG. 2) of this embodiment. As shown in FIG. 8, the Stirling refrigerator 100 according to the present embodiment is different from the refrigerator 100 according to the first embodiment with respect to the seal mechanism 15.

  Specifically, as shown in FIG. 8, in the sealing mechanism 15 of the present embodiment example, the flow equalization promoting means 150 includes a circumferential flow passage 151 and a plurality (eight) of dispersion opening passages 156. Is done. The number of dispersion opening passages 156 is not limited to eight. In addition, the number of dispersion passages 156 and the flow path diameter thereof can be optimized after taking into account the dead volume in the seal mechanism 15.

  As shown in FIG. 8, the dispersion opening passage 156 is formed in the seal mechanism 15 along the major axis Y direction of the seal mechanism 15, one end communicating with the circumferential flow passage 151, and the other end communicating with the compression space C. is doing. Moreover, the dispersion | distribution opening channel | path 156 is opened facing the heat exchange part 14 (shown in FIG. 2).

  As described above, in the Stirling refrigerator 100 according to the embodiment, the flow equalization promoting unit 150 communicates with the circumferential flow passage 151 and the circumferential flow passage that flow in the circumferential direction of the seal mechanism 15, and communicates with the heat exchange unit 14. By providing a plurality of dispersive opening passages 156 that face each other, the working fluid flowing from the working fluid introduction portion 1204 to the seal mechanism 15 flows along the circumferential flow passage 151 of the seal mechanism 15 around the seal mechanism 15. It can flow as evenly as possible in the entire direction. Further, the working fluid is discharged from the circumferential flow passage 151 through the plurality of dispersed opening passages 156 so as to face the heat exchange unit 14 disposed between the cylinder 11 (shown in FIG. 2) and the case unit 120. be able to. That is, the working fluid flowing in the circumferential direction of the seal mechanism 15 can be distributed and flowed to the heat exchange unit 14 as uniformly as possible through the plurality of dispersion opening passages 156. Thereby, heat exchange is accelerated | stimulated as uniformly as possible, and the efficiency of the freezing part 1 (shown in FIG. 2) can be improved.

  Further, the plurality of dispersion opening passages 156 of the Stirling refrigerator 100 of the present embodiment are formed in the seal mechanism 15 symmetrically and equidistantly with the axis of the major axis Y of the case portion 120 as the axis of symmetry. It is preferable. By forming the dispersion opening passage 156 symmetrically and equidistantly in the seal mechanism 15, the working fluid that has flowed through the circumferential flow passage 151 formed in the seal mechanism 15 flows into the flow passages of the plurality of dispersion opening passages 156. It is distributed and guided and distributed to the heat exchanging section 14 as evenly as possible. Further, since the plurality of dispersed opening passages 156 are arranged symmetrically and equidistantly, the pressure of the working fluid in the circumferential flow passage 151 of the seal mechanism 15 can be made as uniform as possible.

(Fourth embodiment)
This embodiment is basically the same as the configuration of the third embodiment. Hereinafter, a different part from the third embodiment will be described. Note that portions similar to those in the third embodiment are described using the same reference numerals.

  FIG. 9 shows the sealing mechanism 15 of the Stirling refrigerator 100 (shown in FIG. 2) of this embodiment. As shown in FIG. 9, the Stirling refrigerator 100 according to the present embodiment is different from the refrigerator 100 according to the third embodiment with respect to the flow equalization promoting means 150.

  Specifically, as shown in FIG. 9, the flow equalization promoting means 150 of the present embodiment includes a circumferential flow passage 151, eight dispersion opening passages 156, and a mesh 157. The number of dispersion opening passages 156 is not limited to eight. In addition, the number of dispersion passages 156 and the flow path diameter thereof can be optimized after taking into account the dead volume in the seal mechanism 15.

  As shown in FIG. 9, the mesh 157 is installed between the heat exchange unit 14 and the seal mechanism 15 in the compression space C, and rectifies the flow of the working fluid. Note that the mesh 157 constitutes the rectification unit of the Stirling refrigerator 100 of the present invention.

  By providing the mesh 157 between the seal mechanism 15 and the heat exchange unit 14, the working fluid can flow to the heat exchange unit 14 as uniformly as possible. That is, the working fluid flowing into the compression space C through the plurality of dispersion opening passages 156 is further promoted by the mesh 157, and can flow into the heat exchange unit 14 (shown in FIG. 2) as evenly as possible. Therefore, the working fluid can flow through almost the entire heat exchanging section 14, heat exchange is promoted as uniformly as possible, and the efficiency of the refrigeration section 1 (shown in FIG. 2) can be improved. This is advantageous for improving the efficiency of the entire refrigerator 100.

(Other)
Each of the above-described exemplary embodiments has been described with the refrigerator 900 as the refrigerated side. However, the embodiment is not limited to the refrigerator 900 but is applied to industrial equipment (for example, an engine).

  The Stirling refrigerator of the present invention can be used, for example, in the field of cooling (freezing) such as household or commercial refrigerators.

It is a conceptual diagram (side view) of the refrigerator which attached the Stirling refrigerator in the example of 1st Embodiment of this invention. It is a conceptual diagram (sectional view) of the Stirling refrigerator in the first embodiment of the present invention. It is an enlarged view near the seal mechanism of the Stirling refrigerator in the first embodiment of the present invention. It is sectional drawing of the II position of the sealing mechanism of the Stirling refrigerator shown in FIG. The state which attached the case part of the Stirling refrigerator in the example of 1st Embodiment of this invention to the refrigerator is shown. As a comparative example, a state in which a case portion of a conventional refrigerator is attached to a refrigerator is shown. It is sectional drawing (II position shown in FIG. 3) of the sealing mechanism of the Stirling refrigerator in the example of 2nd Embodiment of this invention. It is a three-dimensional view showing the sealing mechanism of the Stirling refrigerator in the third embodiment of the present invention. It is a three-dimensional view showing the sealing mechanism of the Stirling refrigerator in the fourth embodiment of the present invention. It is a conceptual diagram of the conventional integrated Stirling refrigerator concerning patent document 1. FIG. It is a conceptual diagram of the conventional Stirling refrigerator which concerns on patent document 2. FIG. It is a conceptual diagram of the conventional Stirling refrigerator concerning patent document 3. FIG. It is a conceptual diagram of the conventional Stirling refrigerator. It is sectional drawing of the II-II position of the conventional Stirling refrigerator shown in FIG.

Explanation of symbols

1: Refrigeration unit 2: Connection passage 3: Compressor
11: Cylinder (heat exchange means)
13: Displacer (heat exchange means)
14: Heat exchange part (heat exchange means)
101: Freezing generator (internal space)
15: Sealing mechanism 150: Flow equalization promoting means 120: Case part 1201: Sealed end part 1204: Working fluid introduction part E: Expansion space C: Compression space

Claims (11)

A case portion having a sealed end portion at least at one end;
A seal mechanism that is housed in the case part and forms an internal space in which a working fluid is sealed between the sealed end part;
An expansion space installed in the internal space for expanding the working fluid and a compression space for compressing the working fluid;
A compressor that is located outside the case portion and generates pressure fluctuations with respect to the working fluid;
Heat exchange means for exchanging heat by reciprocating the working fluid between the expansion space and the compression space;
The sealing mechanism is
A working fluid introduction section for introducing the working fluid flowing from the compressor into the seal mechanism;
A Stirling refrigerator, comprising: current equalization promoting means for promoting equalization of the working fluid introduced from the working fluid introduction section and diverting to the heat exchange means.   The heat exchanging means is accommodated between the cylinder and the case part, a cylinder accommodated in the internal space and arranged coaxially with the case part, a displacer slidably mounted on the cylinder, and the cylinder and the case part. A heat exchanging unit composed of a heat exchanger and a regenerator, wherein the expansion space is formed between the sealed end and the heat exchanging unit, and the compression space is formed between the heat exchanging unit and the heat exchanging unit. 2. The Stirling refrigerator according to claim 1, wherein the Stirling refrigerator is formed between a seal mechanism and a compressor that is located outside the case portion and generates pressure fluctuations with respect to the working gas.   The Stirling refrigerator according to any one of claims 1 and 2, further comprising a connecting passage that communicates the compressor and the working fluid introduction section. The flow equalization promoting means is
A central opening passage formed in the sealing mechanism and opening in a central portion of the compression space along a longitudinal direction of the case portion;
A circumferential flow passage formed in the seal mechanism and allowing the working fluid flowing from the compressor through the working fluid introduction portion to flow along a circumferential direction of the seal mechanism;
A plurality of dispersion passages formed along the radial direction of the seal mechanism, with one end communicating with the circumferential flow passage and the other end communicating with the central opening passage;
The working fluid that has flowed into the seal mechanism from the compressor is gathered in the central portion of the compression space via the circumferential flow passage, the plurality of dispersion passages, and the central opening passage, and the central portion The Stirling refrigerator according to any one of claims 1 to 3, wherein the Stirling refrigerator flows through the heat exchanger.   5. The Stirling refrigerator according to claim 4, wherein the plurality of dispersion passages are formed in the seal mechanism symmetrically and equidistantly with a long axis of the case portion as a symmetry axis.   The sealing mechanism includes an opposing end facing the compression space, and the opposing end includes an inclined surface that is centered on the long axis of the case portion and rises in a direction from the center toward the outer periphery. The Stirling refrigerator according to any one of claims 4 and 5. The flow equalization promoting means is
A circumferential flow passage formed in the seal mechanism and allowing the working fluid flowing from the compressor through the working fluid introduction portion to flow along a circumferential direction of the seal mechanism;
A plurality of dispersion openings formed along the major axis direction of the seal mechanism, one end communicating with the circumferential flow passage, the other end communicating with the compression space, and opening facing the heat exchange portion A passage,
The said working fluid which flowed in in the said case part from the said compressor flows into the said heat exchange part through the said circumferential flow path and these dispersion | distribution opening passages, Any one of Claims 1-3 characterized by the above-mentioned. The Stirling refrigerator according to claim 1.   8. The Stirling refrigerator according to claim 7, wherein the plurality of distributed opening passages are formed symmetrically and equidistantly in the seal mechanism with a long axis of the case portion as a symmetric axis. .   9. The Stirling according to claim 7, wherein the flow equalization promoting unit includes a rectifying unit that rectifies the flow of the working fluid between the heat exchange unit and the seal mechanism. refrigerator.   The Stirling refrigerator according to any one of claims 1 to 9, wherein the heat exchange means absorbs heat from the side to be frozen through the sealed end portion. The to-be-frozen side is a refrigerator provided with a freezer compartment,
The Stirling refrigerator according to claim 10, wherein the sealed end portion is installed in the freezer compartment of the refrigerator.

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