JP2020016349A - Stirling refrigerator and refrigerator - Google Patents

Abstract

To provide a stirling refrigerator capable of giving desired phase difference to reciprocating motions of a piston for compression and a piston for inflation while linearly arranging a cylinder for compression and a cylinder for inflation.SOLUTION: A stirling refrigerator includes: a swash plate shaft connected to a motor and extending in a prescribed axial direction; a swash plate for compression diagonally fitted to the swash plate shaft; a piston for compression provided in the way that it moves reciprocatingly in the axial direction by rotation of the swash plate for compression; a cylinder for compression where working fluid is compressed by the piston for compression; a swash plate for inflation diagonally fitted to the swash plate shaft; a piston for inflation moving reciprocatingly in the axial direction by rotation of the swash plate for inflation; and a cylinder for inflation which is arranged side by side with the cylinder for compression in the axial direction and inflates the working fluid compressed by the cylinder for compression. Both the swash plate for compression and the swash plate for inflation are provided for the swash plate shaft with prescribed phase difference.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a Stirling refrigerator.

  Energy saving of refrigerators that are energized all day is urgently needed as part of global environmental protection and global warming countermeasures. From the viewpoint of such energy saving measures, the use of a Stirling refrigerator instead of an evaporative refrigeration cycle in a refrigerator has been studied.

  As a Stirling refrigerator, one swash plate is provided for a swash plate shaft rotated by a motor, and the rotation of the swash plate reciprocates both a compression piston and an expansion piston to compress a working fluid in a compression cylinder. In addition, there is one in which the expansion by an expansion cylinder is repeated (see Patent Document 1).

JP-A-11-287525

  However, such a conventional Stirling refrigeration cycle has the following problems.

  1. In the conventional swash plate type Stirling refrigerator, since the compression piston and the expansion piston are provided for one swash plate, the phase difference is fixed by the arrangement of each piston in the circumferential direction. Therefore, it is difficult to optimally design the Stirling refrigeration cycle so as to realize the best refrigeration efficiency.

  2. In order to provide an ideal phase difference between the compression piston and the expansion piston, the compression cylinder and the expansion cylinder are arranged at positions shifted in the circumferential direction, and are separately connected so that the working fluid can flow between the cylinders. Must be connected by piping. For this reason, the connecting pipe becomes long, the dead volume, which is a useless volume that does not contribute to the compression and expansion of the working fluid, increases, and the output greatly decreases.

  3. In addition, there is another problem that the Stirling refrigeration cycle itself is increased in size by providing the connecting pipe.

  4. Further, if the flow path length of the connecting pipe is long, the flow loss of the working fluid also occurs, so that the performance also deteriorates.

  5. In addition, since an ideal phase difference is generated in the reciprocating motion of each piston by the arrangement of each cylinder, the cylinder arrangement is almost fixed. Therefore, it is difficult to freely design the number of sets of each cylinder while maintaining the phase difference.

  Therefore, an object of the present invention is to provide a Stirling refrigerator capable of solving the above problems at once.

  That is, the Stirling refrigerator according to the present invention includes a swash plate shaft connected to a motor and extending in a predetermined axial direction, a compression swash plate obliquely attached to the swash plate shaft, and a compression swash plate. , A compression piston provided to reciprocate in the axial direction, a compression cylinder in which a working fluid is compressed by the compression piston, and an expansion obliquely attached to the swash plate axis. A swash plate, an expansion piston provided to reciprocate in the axial direction by the rotation of the expansion swash plate, and a compression cylinder disposed in the axial direction along with the compression cylinder. An expansion cylinder for expanding the compressed working fluid, wherein the compression swash plate and the expansion swash plate are provided on the swash plate shaft with a predetermined phase difference.

  With such a configuration, a desired phase difference can be set in the reciprocating motion of the compression piston and the expansion piston by the phase difference between the compression swash plate and the expansion swash plate. For this reason, since the arrangement of the compression cylinder and the expansion cylinder is not restricted by the set phase difference, the compression cylinder and the expansion cylinder can be arranged side by side in the axial direction.

  Therefore, it is not necessary to dispose the compression cylinder and the expansion cylinder at a predetermined angle in the circumferential direction as in the related art, so that the flow path through which the working fluid flows between the compression cylinder and the expansion cylinder is smaller than before. Can also be shortened. Therefore, the dead volume can be reduced, the flow loss of the working fluid can be reduced, and the device itself can be configured to be small while having high efficiency.

  Further, since the compression cylinders and the expansion cylinders are arranged in a line, the number of sets of each cylinder can be set freely as compared with the conventional case, and it is easy to realize an optimal design.

  As a preferable range of the phase difference between the compression swash plate and the expansion swash plate that can realize high efficiency as a Stirling refrigerator, the phase difference between the compression swash plate and the expansion swash plate is 80 ° or more and 100 ° or less. That are set to.

  As a Stirling refrigerator in which a more preferable phase difference is formed from the viewpoint of efficiency, there is a Stirling refrigerator in which the phase difference between the compression swash plate and the expansion swash plate is substantially 90 °.

  In order to make the flow path length of the working fluid flowing between the compression cylinder and the expansion cylinder as short as possible and to increase the refrigeration efficiency, the working fluid compressed by the compression cylinder radiates heat to the outside. Heater, a cooler in which the working fluid expanded in the expansion cylinder absorbs heat from the outside, heat of the working fluid passed through the heater, and heat stored in the working fluid passed through the cooler. A regenerator that raises the temperature, and the heater, the regenerator, and the cooler may be arranged between the compression cylinder and the expansion cylinder in the axial direction.

  Another configuration example that can improve the refrigeration efficiency as compared with the related art includes a heater in which the working fluid compressed by the compression cylinder radiates heat to the outside, and a working fluid expanded by the expansion cylinder absorbs heat from the outside. And a regenerator that stores heat of the working fluid that has passed through the heater and heats up the heat by storing the heat of the working fluid that has passed through the cooler. An example in which the heater, the regenerator, and the cooler are arranged so as to be displaced from the cylinder in the radial direction of the swash plate axis.

  For example, in order to facilitate heat exchange between the air and the working fluid, and to improve the heat exchange performance, the cooler, and the cooler are each configured by a plurality of pipes through which the working fluid flows. It should just be done.

  The cooler, the regenerator, and the heater are arranged in a row using the same member, and in order to simplify the structure, if the regenerator is configured by a plurality of pipes through which a working fluid flows. Good.

  In order to further improve the heat exchange efficiency between the working fluid and the air in the cooler and the heater, it is only necessary that fins are provided on the surface of the pipe.

  A Stirling refrigerator according to the present invention, a refrigerating compartment, a refrigerating compartment, and a controller that performs a revolving speed control to make the revolving speed of the motor different between when the refrigerating compartment is cooled and when the refrigerating compartment is cooled, , It is possible to achieve energy saving while achieving the same cooling capacity as compared with a refrigerator having an evaporative refrigeration cycle. Further, since it is possible to avoid the use of a refrigerant having a high environmental load or a flammable refrigerant, it is possible to exert an effect on environmental load and measures against global warming.

  The Stirling refrigerator according to the present invention, a refrigerator, a refrigerator, a refrigerator of the Stirling refrigerator, a duct connecting between the refrigerator and the refrigerator, and the refrigerator through the duct. A duct switching device that switches a flow path so that air that has passed through the cooler is supplied to either the room or the freezing room, if the refrigerator includes a Stirling refrigerator, the rotation speed of the motor is changed. Even without doing so, the temperature of the refrigerating compartment and the freezing compartment can be maintained at desired temperatures by switching the duct.

  A Stirling refrigerator according to the present invention, a refrigerator, a refrigerator, and a cooler for the Stirling refrigerator, wherein the brine exchanges heat between the air in the refrigerator compartment or the air in the refrigerator compartment via brine. And the circuit, the refrigerator and the freezer can be efficiently cooled by the cooler by the brine.

  If the brine circuit includes a brine pump that circulates brine, the refrigerator can be cooled by circulating brine regardless of the position of the Stirling refrigerator in the refrigerator.

  In order to be able to cool the refrigerator compartment and the freezer compartment with a small power consumption for the circulation of the brine, the Stirling refrigerator is arranged above the refrigerator compartment and the freezer compartment, and the brine is thermally siphoned. It is only necessary that the circuit be configured to circulate through the brine circuit.

  As described above, according to the Stirling refrigerator according to the present invention, the compression swash plate and the expansion swash plate can form a phase difference in the reciprocating motion of the compression piston and the expansion piston. There is no need to form a phase difference with the arrangement of the compression cylinder and the expansion cylinder. For this reason, the compression cylinder and the expansion cylinder are arranged in a line, the flow path of the working fluid is minimized, the dead volume and the flow resistance are reduced, and the device can be downsized. Further, since the compression cylinder and the expansion cylinder through which the working fluid flows are arranged in a line, even if the number of sets of each cylinder is increased, there is little restriction on design, and it is easy to realize an optimal design.

FIG. 1 is a schematic longitudinal sectional view showing a Stirling refrigerator according to a first embodiment of the present invention. The typical longitudinal section showing the Stirling refrigerator concerning a 2nd embodiment of the present invention. The typical longitudinal section and the typical AA line sectional view showing the Stirling refrigerator concerning a 3rd embodiment of the present invention. The schematic longitudinal section showing the Stirling refrigerator concerning the modification of a 3rd embodiment of the present invention, and the line sectional view of typical BB. FIG. 9 is a schematic longitudinal sectional view and a schematic CC sectional view showing a Stirling refrigerator according to a fourth embodiment of the present invention. The schematic diagram which shows the Stirling refrigerator and refrigerator which concern on 5th Embodiment of this invention. The schematic diagram which shows the 1st modification of the Stirling refrigerator and refrigerator which concern on 5th Embodiment of this invention. The schematic diagram which shows the 2nd modification of the Stirling refrigerator and refrigerator which concern on 5th Embodiment of this invention. The schematic diagram which shows the 3rd modification of the Stirling refrigerator and refrigerator which concern on 5th Embodiment of this invention.

  A Stirling refrigerator 100 according to a first embodiment of the present invention will be described with reference to FIG.

  The Stirling refrigerator 100 is used, for example, to generate cool air in a refrigerator. Specifically, the Stirling refrigerator 100 is configured such that a plurality of sets of cylinders and pistons are housed in a substantially cylindrical casing 1 whose inside is sealed, and the working fluid repeats a cycle of compression, heat release, expansion, and heat absorption. It was done. As the working fluid, a fluid having a low critical point and hardly liquefied in the course of the cycle is selected. Specifically, helium, nitrogen, hydrogen, or the like is used as a working fluid.

  That is, the Stirling refrigerator 100 operates by rotating the swash plate shaft 3 that extends in the axial direction AX of the casing 1 and is connected to the motor 2. The Stirling refrigerator 100 includes a compression cylinder 41 that compresses a working fluid filled in the casing 1 by reciprocating motion of a compression piston 42, and a reciprocation of the working fluid compressed by the compression cylinder 41 between an expansion piston 52. An expansion cylinder 51 that expands by movement. In the first embodiment, the compression cylinders 41 and the expansion cylinders 51 are arranged in pairs at every 90 ° in the circumferential direction. Further, a set of the compression cylinder 41 and the expansion cylinder 51 through which the working fluid flows is arranged side by side in the axial direction AX.

  Each of the compression piston 42 and the expansion piston 52 is configured to repeat reciprocating motion with a predetermined phase difference. In the first embodiment, the inner surfaces of the compression piston 42 and the expansion piston 52 are arranged to face each other.

  Specifically, the compression piston 42 is configured to repeat reciprocating motion by a compression swash plate 43 that is obliquely attached to the motor 2 side of the swash plate shaft 3. Specifically, the compression swash plate 43 is attached to the face plate portion so as to be obliquely incident on the axial direction AX of the swash plate shaft 3.

  The expansion piston 52 is configured to repeat a reciprocating motion by an expansion swash plate 53 attached to a tip end side of the swash plate shaft 3. Specifically, the expansion swash plate 53 is attached to the face plate portion so as to be obliquely incident on the axial direction AX of the swash plate shaft 3.

  The swash plate 43 for compression and the swash plate 53 for expansion are arranged such that the working fluid in the compression cylinder 41 and the expansion cylinder 51 arranged in a line in the axial direction AX repeats isothermal compression, isovolumic process, and isothermal expansion. The mounting direction in the circumferential direction with respect to the swash plate shaft 3 is different so as to be repeated. Therefore, the compression swash plate 43 and the expansion swash plate 53 are attached to the swash plate shaft 3 with a predetermined phase difference. In the first embodiment, the phase difference between the compression swash plate 43 and the expansion swash plate 53 is set to 80 ° or more and 100 ° or less. More preferably, the phase difference between the compression swash plate 43 and the expansion swash plate 53 is set to 90 °.

  In the first embodiment, the heater 6, the regenerator 7, and the cooler 8 are arranged between the compression cylinder 41 and the expansion cylinder 51 so as to be aligned in the axial direction AX.

  The heater 6 is a portion that heats the air by radiating the working fluid compressed by the compression cylinder 41 to external air.

  The cooler 8 is a portion that absorbs the heat of the working fluid expanded in the expansion cylinder 51 from external air and cools the air.

  The regenerator 7 is provided between the heater 6 and the cooler 8, absorbs the heat of the working fluid that has passed through the heater 6, stores the heat, and rises with the heat stored in the working fluid that has passed through the cooler 8. Is what warms up.

  In the Stirling refrigerator 100 of the first embodiment configured as described above, the compression cylinder 41, the heater 6, the regenerator 7, the cooler 8, and the expansion cylinder 51 in which the working fluid flows are arranged in a line in the axial direction AX. Since they are arranged side by side, there is no connecting pipe as in the related art. Therefore, the dead volume that does not contribute to the compression and expansion of the working fluid can be minimized. In addition, since the length of the flow path through which the working fluid flows can be minimized, the flow resistance of the working fluid can be suppressed. From these facts, it is possible to improve the cooling efficiency as compared with the conventional one while making the size of the Stirling refrigerator 100 compact.

  Further, a phase difference is formed by making the circumferential mounting directions of the compression swash plate 43 and the expansion swash plate 53 different from each other with respect to the swash plate shaft 3, and the reciprocating motion of the pair of the compression piston 42 and the expansion piston 52 is formed. A phase difference can be formed. Therefore, it is not necessary to form a phase difference by differentiating the circumferential arrangement of the compression cylinder 41 and the expansion cylinder 51 as in the related art, and the compression cylinder 41 and the expansion cylinder 51 are arranged in the axial direction AX. They can be arranged in a row. As described above, the connecting pipe is eliminated by this feature, and the dead volume and the flow path length can be reduced. Further, the compression cylinder 41, the heater 6, the regenerator 7, the cooler 8, and the expansion cylinder 51 can be arranged in a line in the axial direction AX. Is small. Therefore, it is easy to provide not only four sets but also many sets of the compression cylinders 41 and the expansion cylinders 51 as in the first embodiment.

  Further, since two swash plates, the swash plate 43 for compression and the swash plate 53 for expansion, are provided, the mounting can be adjusted separately, and the phase difference of each swash plate and the compression piston 42 and the expansion swash plate 53 can be freely adjusted. The phase difference of the reciprocating motion of the piston 52 can be adjusted. For this reason, for example, it is easy to realize a phase difference that provides the best cooling efficiency.

  Next, a Stirling refrigerator 100 according to a second embodiment will be described with reference to FIG. The members corresponding to the members described in the first embodiment are denoted by the same reference numerals.

  In the Stirling refrigerator 100 of the second embodiment, a heater 6, a regenerator 7, and a cooler 8 are provided in a line between a compression cylinder 41 and an expansion cylinder 51 as in the first embodiment. And are shifted in the radial direction. The compression piston 42 and the expansion piston 52 are arranged so that the inner surfaces thereof face outward.

  Specifically, in the second embodiment, the heater 6, the regenerator 7, and the cooler 8 are arranged side by side in the casing 1 radially outside the compression cylinder 41 and the expansion cylinder 51. The working fluid compressed in the compression cylinder 41 first moves to the motor 2 side opposite to the expansion cylinder 51 and passes through the heater 6, the cooler 8, and the cooler 8 arranged on the outer peripheral side. From the tip side into the expansion cylinder 51. The working fluid expanded in the expansion cylinder 51 returns to the compression cylinder 41 in a reverse route.

  The phase difference of the reciprocating motion of the compression piston 42 and the expansion piston 52 is determined by the phase difference depending on the mounting direction of the compression swash plate 43 and the expansion swash plate 53 with respect to the swash plate shaft 3 as in the first embodiment. Adjusted.

  In the Stirling refrigerator 100 of the second embodiment configured as described above, the phase difference of the operation required during the cycle is caused by the phase difference between the compression swash plate 43 and the expansion swash plate 53 as in the first embodiment. Can be set. Further, as in the first embodiment, the set of the compression cylinder 41 and the expansion cylinder 51 through which the working fluid flows can be arranged in the axial direction AX. Therefore, even when a plurality of sets of the compression cylinder 41 and the expansion cylinder 51 are provided in the casing 1, the arrangement is not limited by the phase difference to be set, and the optimum design is easy.

  Furthermore, since the flow path through which the working fluid flows can be formed only in the casing 1, there is no need to provide a connecting pipe having a portion extending in the radial direction of the casing 1, unlike the conventional case. Volume and flow resistance can be reduced.

  Further, since the heater 6 and the cooler 8 can be arranged on the outer peripheral side of the casing 1, the area of heat exchange with external air via the casing 1 can be made larger than in the first embodiment, The amount of heat exchange can be increased.

  Next, a Stirling refrigerator 100 of a third embodiment will be described with reference to FIG. The members corresponding to the members described in the first embodiment are denoted by the same reference numerals. In addition, FIG. 3 shows not only a longitudinal sectional view but also a sectional view taken along line AA.

  The Stirling refrigerator 100 of the third embodiment is different from the first embodiment in the configuration of the heater 6, the regenerator 7, and the cooler 8. Specifically, the heater 6, the regenerator 7, and the cooler 8 are each formed of a plurality of pipes P through which a working fluid flows. Further, the heater 6 and the cooler 8 are arranged at the cut portions of the casing 1 so that the outer surfaces of the plurality of pipes P can directly contact the outside air to increase the surface area contributing to heat exchange. Is configured.

  In the Stirling refrigerator 100 of the third embodiment, the amount of heat exchange between the working fluid and the external air in the heater 6 and the cooler 8 is further increased, and the refrigeration efficiency is improved. Can be.

  In addition, since the heater 6, the regenerator 7, and the cooler 8 are each formed of a cylindrical pipe P, and are arranged in a line in the axial direction AX, the assemblability can be improved.

  Next, a modification of the third embodiment will be described with reference to FIG. Note that FIG. 4 shows not only a longitudinal sectional view but also a sectional view taken along line BB.

  As shown in FIG. 4, only the heater 6 and the cooler 8 may be formed by a plurality of pipes P, and the regenerator 7 may not be formed by the pipes P. Even in such a case, it is possible to increase the surface area where the heat exchange between the working fluid and the air can be performed, thereby improving the heat exchange efficiency.

  Next, a Stirling refrigerator 100 of a fourth embodiment will be described with reference to FIG. Note that members corresponding to those described in the first and third embodiments are denoted by the same reference numerals. In addition, FIG. 5 shows not only a longitudinal sectional view but also a sectional view taken along line CC.

  In the Stirling refrigerator 100 of the fourth embodiment, a plurality of annular fins F are provided on the outer surface of each pipe P in the heater 6 and the cooler 8 formed by the plurality of pipes P.

  Thus, in the heater 6 and the cooler 8 of the fourth embodiment, the surface area contributing to the heat exchange can be further increased, and the heat exchange efficiency can be increased.

  Next, a refrigerator 200 according to a fifth embodiment of the present invention will be described with reference to FIG. In the refrigerator 200 of the fifth embodiment, any one of the Stirling refrigerators 100 described in the first to fourth embodiments is used.

  As shown in FIG. 6, the refrigerator 200 includes a refrigerator room maintained at a predetermined temperature, a freezer room maintained at a lower temperature than the refrigerator room, and a machine room accommodating various devices such as the Stirling refrigerator 100. , Is provided. A duct (not shown) is provided between the machine room, the refrigerator room, and the freezer room, and air cooled by the Stirling refrigerator 100 in the machine room can be supplied to one of the refrigerator room or the freezer room through the duct. It is configured as follows. That is, the refrigerator 200 is a direct cooling refrigerator 200 that directly cools air.

  In the fifth embodiment, a control unit COM for controlling the number of rotations of the motor 2 of the Stirling refrigerator 100 is further provided, and the number of rotations of the motor 2 is made different between when the refrigerator is cooled and when the freezer is cooled. It is configured as follows. That is, when the freezer compartment is cooled more than when the refrigerator compartment is cooled, the rotation speed of the motor 2 is increased to increase the cooling amount of air, and the temperature of the freezer compartment is further reduced. Specifically, the function of the control unit COM is realized by, for example, a computer including a CPU, a memory, an A / D converter, a D / A converter, and various input / output devices. That is, the refrigerator program stored in the memory is executed, and a function as the control unit COM is realized by cooperation of various devices.

  With the refrigerator 200 including such a Stirling refrigerator 100, it is possible to achieve energy saving while achieving the same cooling capacity as compared with the refrigerator 200 including the evaporative refrigeration cycle. Further, since it is possible to avoid the use of a refrigerant having a high environmental load or a flammable refrigerant, it is possible to exert an effect on environmental load and measures against global warming.

  Next, a modification of the fifth embodiment will be described with reference to FIGS.

  In the refrigerator 200 of the modification shown in FIG. 7, the rotation speed of the motor 2 of the Stirling refrigerator 100 is not changed between the time of cooling the refrigerator compartment and the time of cooling the freezer room, and the motor 2 is operated at a constant speed and the duct D is switched Is configured to control the temperature in each room.

  Specifically, the duct D is configured such that the airflow passes through a cooler 8 composed of a number of pipes P having fins F formed on the outer periphery in the Stirling refrigerator 100. That is, the duct D connects the cool air discharge passage D1 connecting the cooler 8 and the duct switching device DS, and connects the duct switching device DS and the refrigerating room, and supplies cool air to the refrigerating room. A first cool air supply passage D2, a connection between the refrigerator compartment and the cooler 8, a first return passage D3 for returning air in the refrigerator compartment from the refrigerator compartment to the suction side of the cooler 8, and a duct switching device DS A second cool air supply passage D4 for supplying cool air to the freezing room, and a freezing room and a cooler 8 connected between the freezing room and the cooler 8; And a second return flow path for returning the air in the freezer to the second return passage.

  The duct switching device DS includes a cooler 8, a cool air discharge flow path D1, a first cool air supply flow path D2, a refrigerator, a first return flow path D3, and a first circulation path for circulating an air flow in the order of the cooler 8. , The cooler 8, the cool air discharge flow path D 1, the second cool air supply flow path D 4, the freezing compartment, the second return flow path D 5, and the cooler 8. Or the flow path is switched so that air does not flow through any of them.

  The switching timing of the operation of the duct switching device DS is controlled by, for example, the temperature in the refrigerator compartment or the freezer compartment. That is, the duct switching device DS first circulates air in the first circulation path, and when the inside of the refrigerator reaches the first predetermined low temperature, switches so that air circulates in the second circulation path, and starts cooling the freezing room. . When the temperature of the freezing room becomes the second predetermined low temperature, the duct switching device DS suspends the circulation of the air so that the air does not circulate in either the refrigerator room or the freezing room. Then, when the temperature in the freezer compartment reaches a predetermined high temperature, the tongue operation is repeated again.

  Even in such a case, the Stirling refrigerating apparatus 100 can keep the refrigerator compartment and the freezer compartment in a predetermined temperature range.

  The refrigerator 200 of the modification shown in FIG. 8 is configured to be able to cool the refrigerator compartment and the freezer compartment using brine. Specifically, the refrigerator 200 is configured such that the brine circulates between the cooler 8 of the Stirling refrigerator 100 and the heat exchanger 94 or the heat exchanger 95 provided in the refrigerator or freezer. Is provided. That is, the refrigerator 200 of this modified example is a secondary cooling type refrigerator 200 that cools the air in the refrigerator with brine.

  The brine circuit 9 includes a brine heat exchanger 91 that performs heat exchange between the cooler 8 of the Stirling refrigerator 100 and the brine, a brine pump 92 that circulates the brine in the brine circuit 9, and a refrigerator indoor heat exchanger 94. And a switching valve 93 for switching the brine so as to flow to any of the freezer indoor heat exchangers 95. The brine heat exchanger is formed of a flat tube, and is wound around the outer periphery of the cooler 8 of the Stirling refrigerator 100.

  In such a case, by controlling the discharge amount of the pump 92 and the switching valve 93 while operating the Stirling refrigerator 100 at a constant rotation speed, it is possible to keep the refrigerator compartment and the freezer compartment at different temperatures. Becomes possible.

  In the refrigerator 200 of the modified example shown in FIG. 9, the brine circuit 9 is not provided with the pump 92 for flowing the brine, and the brine is circulated by the thermal siphon.

  Specifically, as shown in FIG. 9, the machine room is disposed above the refrigerator room and the freezing room, and brine cooled and liquefied by the Stirling refrigerator 100 located above and becoming heavier is located below the refrigerator. It flows into the indoor heat exchanger 94 or the freezing indoor heat exchanger 95. In the refrigerator compartment heat exchanger 94 or the freezer compartment heat exchanger 95, heat exchange occurs between the air in the refrigerator and the brine, and the brine is vaporized. On the other hand, in the brine heat exchanger 91 located above, the vaporized brine is cooled and liquefied by the Stirling refrigerator 100, so that a pressure drop occurs in the brine heat exchanger 91. Due to this pressure drop, the brine vaporized in the refrigerator indoor heat exchanger 94 or the freezer indoor heat exchanger 95 is sucked into the brine heat exchanger 91 located above. Thus, in the brine circuit 9, the vaporized brine present at the lower portion flows into the upper portion, and the brine returns to the brine heat exchanger 91.

  In such a case, since the pump 92 for flowing the brine is not required, power saving can be realized accordingly. Further, by changing the length of time during which the brine is supplied to the refrigerating compartment or the freezing compartment by controlling the switching valve 93, it is possible to maintain different temperatures.

  Other embodiments will be described.

  The Stirling refrigerator described in each embodiment has been described mainly for the case where it is used for a refrigerator, but may be used for other purposes. For example, the Stirling refrigerator according to the present invention may be used as a car air conditioner or another air conditioner.

  Further, the Stirling refrigerator may be used not only for cooling but also as a heat pump for heating air or brine by a heater.

  Although the number of sets of compression cylinders and expansion cylinders shown in each embodiment is four, more sets of compression cylinders and expansion cylinders are provided to further increase the cooling amount as one Stirling refrigerator. It does not matter. The number of sets may be set as appropriate according to the purpose or purpose. For example, a set of compression cylinders and expansion cylinders may be arranged side by side at 45 ° in the circumferential direction, and eight sets of compression cylinders and expansion cylinders may be arranged in the casing. Conversely, the number of compression cylinders and expansion cylinders may be reduced to one, two, or three.

  The configurations of the heater, the regenerator, and the cooler are not limited to the configurations described in each embodiment. Other known configurations may be used.

  In addition, a part of each embodiment may be modified, or a part or all of each embodiment may be combined, as long as it does not contradict the spirit of the present invention.

200 refrigerator 100 Stirling refrigerator 1 casing 2 motor 3 swash plate shaft 41 compression cylinder 42 compression piston 43 compression oblique Plate 51 ... Expansion cylinder 52 ... Expansion piston 53 ... Expansion swash plate 6 ... Heater 7 ... Regenerator 8 ... Cooler 9 ... Brine circuit 91 ... Brine heat exchanger 92 Pump 93 Switching valve 94 Heat exchanger 95 inside refrigerator 95 Heat exchanger COM inside freezer Control unit P Pipe F Pipe fin AX ... axial direction

Claims (13)

A swash plate shaft connected to the motor and extending in a predetermined axial direction;
A compression swash plate attached obliquely to the swash plate axis,
By the rotation of the compression swash plate, a compression piston provided to reciprocate in the axial direction,
A compression cylinder in which a working fluid is compressed by the compression piston;
An expansion swash plate obliquely attached to the swash plate axis,
By the rotation of the expansion swash plate, an expansion piston provided to reciprocate in the axial direction,
An expansion cylinder, which is arranged side by side in the axial direction with the compression cylinder and expands the working fluid compressed by the compression cylinder,
A Stirling refrigerator wherein the swash plate for compression and the swash plate for expansion are provided on the swash plate shaft with a predetermined phase difference.   2. The Stirling refrigerator according to claim 1, wherein a phase difference between the compression swash plate and the expansion swash plate is set to 80 ° or more and 100 ° or less.   The Stirling refrigerator according to claim 1, wherein a phase difference between the compression swash plate and the expansion swash plate is approximately 90 °. A heater in which the working fluid compressed by the compression cylinder radiates heat to the outside,
A cooler in which the working fluid expanded by the expansion cylinder absorbs heat from the outside,
A regenerator that stores heat of the working fluid that has passed through the heater, and raises the temperature with the heat that has stored the working fluid that has passed through the cooler,
The Stirling refrigerator according to any one of claims 1 to 3, wherein the heater, the regenerator, and the cooler are arranged in the axial direction between the compression cylinder and the expansion cylinder. A heater in which the working fluid compressed by the compression cylinder radiates heat to the outside,
A cooler in which the working fluid expanded by the expansion cylinder absorbs heat from the outside,
A regenerator that stores heat of the working fluid that has passed through the heater, and raises the temperature with the heat that has stored the working fluid that has passed through the cooler,
The Stirling refrigerating machine according to any one of claims 1 to 3, wherein the heater, the regenerator, and the cooler are arranged in a radial direction of the swash plate axis with respect to the compression cylinder and the expansion cylinder. Machine.   The Stirling refrigerator according to claim 4 or 5, wherein the cooler and the cooler each include a plurality of pipes through which a working fluid flows.   The Stirling refrigerator according to claim 6, wherein the regenerator includes a plurality of pipes through which a working fluid flows.   The Stirling refrigerator according to claim 6, wherein a fin is provided on the surface of the pipe. A Stirling refrigerator according to any one of claims 1 to 8,
Refrigerator room,
Freezer compartment,
A refrigerator comprising: a control unit that performs rotation speed control that varies the rotation speed of the motor between when the refrigerator compartment is cooled and when the freezer compartment is cooled. A Stirling refrigerator according to any one of claims 1 to 8,
Refrigerator room,
Freezer compartment,
The cooler of the Stirling refrigerator, and a duct connecting between the refrigerator compartment and the freezer compartment,
A duct switching device that switches a flow path so that air that has passed through the cooler is supplied to either the refrigerator compartment or the freezer compartment via the duct. A Stirling refrigerator according to any one of claims 1 to 8,
Refrigerator room,
Freezer compartment,
A refrigerator comprising: the cooler of the Stirling refrigerator; and a brine circuit that exchanges heat between the air in the refrigerator compartment or the air in the refrigerator compartment via brine.   The refrigerator according to claim 11, wherein the brine circuit includes a brine pump that circulates brine. The Stirling refrigerator is disposed above the refrigerator compartment and the freezer compartment,
The refrigerator of claim 11, wherein the brine is configured to circulate through the brine circuit by a thermal siphon.