JP2009191669A - Stirring cycle device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide higher engine efficiency by effectively agitating gas in an expansion space by strengthening a force of the gas blown off to the expansion space. <P>SOLUTION: A cylinder 4 is provided with a jet mechanism for jetting the gas to the expansion space 8. The jet mechanism has a pressure accumulating space 15 having a gas inflow port 16 and a gas outflow port 17 opening in the expansion space 8. The pressure accumulating space 15 receives the gas via the gas inflow port 16 when pressure is high in the expansion space 8, and jets the gas via a gas jetting port 17 when the pressure becomes low in the expansion space 8. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a Stirling cycle apparatus.

  A Stirling cycle device, known as an external combustion engine, that converts heat into power in the Stirling cycle or converts power into heat in the reverse Stirling cycle has been developed in recent years, and there are many examples that are put into practical use. Yes. There are many literature examples, and Patent Document 1 can be cited as an example. Patent Document 1 describes a two-cylinder Stirling cycle apparatus called α type, which is used as a refrigeration apparatus.

As a customary heat engine, the Stirling cycle device is required to constantly improve the efficiency, and therefore, many devices have been devised. In the refrigeration apparatus described in Patent Document 1, the expansion displacer has a built-in regenerator, and a gas turbulence generator that disturbs the flow of gas blown into the expansion space is provided at the inlet / outlet on the expansion space side of the regenerator. Yes. Thus, the inside of the expansion space that generates a low temperature is agitated so that heat transfer between the low temperature gas in the expansion space and the inner wall surface of the expansion cylinder can be performed smoothly, thereby improving the refrigeration effect.
JP-A-8-152215 (paragraphs [0017], [0024], FIGS. 1, 2, 3, 6)

  The refrigeration apparatus described in Patent Document 1 blows out gas taken in from one end of the displacer as it is from the other end of the displacer, and it cannot be said that the blowing force is strong, and it is difficult to expect a strong turbulent flow effect. . Also, this method cannot promote heat transfer in the compression space.

  The present invention has been made in view of this point, and the momentum of the gas blown into the expansion space or the compression space is increased to effectively agitate the gas in the expansion space or the compression space, so that higher engine efficiency can be obtained. The purpose is to.

  In order to achieve the above object, according to the present invention, a piston and a displacer are reciprocated with a phase difference from each other in a cylinder by a power source, and gas flow through the regenerator generated thereby causes one end face of the displacer to be a surface. In the Stirling cycle device that absorbs heat in the expansion space that heats and dissipates heat in the compression space that faces one end surface of the piston, the cylinder is provided with a jet mechanism that jets gas into the expansion space or the compression space. It is said.

  According to this configuration, since the jet mechanism is provided in the cylinder, it is possible to effectively stir the gas without creating channel resistance in the main channel, and higher engine efficiency can be obtained.

  Further, the present invention is the Stirling cycle device having the above-described configuration, wherein the jet mechanism has a pressure accumulation space having a gas inlet and a gas outlet opening to the expansion space or the compression space, and the pressure accumulation space is the expansion space. Gas is received through the gas inlet when the pressure of the space or the compression space is higher, and gas is jetted through the gas outlet when the pressure of the expansion space or the compression space is lower. It is said.

  According to this configuration, the gas taken into the pressure accumulating space can effectively stir the gas in the expansion space or the compression space, and higher engine efficiency can be obtained.

  Further, the present invention is the Stirling cycle device configured as described above, further comprising a heat absorbing member provided with an inner surface in contact with the expansion space or a heat radiating member provided with an inner surface in contact with the compression space. It is characterized by having a nozzle shape protruding toward the inner surface of the heat absorbing member or the heat radiating member.

  According to this configuration, since the gas taken into the pressure accumulation space is further brought closer to the heat absorbing member or the heat radiating member by the nozzle, the heat transfer coefficient in the vicinity of the heat absorbing member or the heat radiating member is promoted, and higher engine efficiency can be obtained.

  According to the present invention, in the Stirling cycle apparatus having the above-described configuration, the gas ejection port is disposed such that the ejection gas flow is substantially perpendicular to the inner surface of the heat absorbing member or the heat radiating member.

  According to this configuration, the gas ejection is substantially perpendicular to the inner surface of the heat absorbing member or the heat radiating member that exchanges heat with the outside, so that not only the gas in the expansion space or the compression space is stirred, but also the high-speed flow of the jet flow Therefore, the gas near the inner surface of the heat radiating member or the heat absorbing member can be effectively disturbed to improve the heat transfer coefficient near the heat radiating member or the heat absorbing member.

  According to the present invention, in the Stirling cycle apparatus configured as described above, a one-way valve for preventing gas from flowing out of the pressure accumulating space is disposed at the gas inlet.

  According to this configuration, it is possible to prevent the backflow of the gas taken into the pressure accumulating space and prevent the pressure in the pressure accumulating space from decreasing before jetting the gas into the working space.

  Further, in the Stirling cycle apparatus having the above-described configuration, the one-way valve that opens when a pressure difference between the pressure accumulation space and the expansion space or the compression space becomes a predetermined value or more is disposed at the gas ejection port. It is characterized by being.

  According to this configuration, when the pressure in the working space is slightly lower than the pressure in the pressure accumulating space, gas is not released to the working space, but when the pressure difference between the pressure accumulating space and the working space becomes a predetermined value or more, one direction Since the valve is opened and the gas is ejected, the force of the ejected gas is increased and the force for generating the jet is increased, so that higher engine efficiency can be obtained. Further, since gas leakage from the gas outlet does not become a problem, the diameter of the gas outlet can be increased, the jet flow rate can be increased, and the heat transfer rate can be greatly improved.

  According to the present invention, instead of immediately blowing out the gas taken into the cylinder, the gas is taken into the pressure accumulation space in the cylinder when the pressure in the expansion space or the compression space is higher, and the gas is taken into the expansion space or the compression space. Since the pressure is blown into the expansion space or compression space when the pressure becomes lower, the momentum of the gas blown out is strengthened, the gas in the expansion space or compression space is effectively disturbed, and the efficiency as a heat engine Can be further enhanced.

  A first embodiment of the present invention will be described with reference to FIGS. 1 to 4. 1 is a cross-sectional view of the Stirling cycle apparatus according to the first embodiment, FIG. 2 is a partial enlarged cross-sectional view of the Stirling cycle apparatus, and FIG. 3 is a partial enlarged cross-sectional view of the Stirling cycle apparatus in a state different from FIG. FIG. 4 is a PV diagram of the reverse Stirling cycle.

  A Stirling cycle apparatus 1 </ b> A shown in FIG. 1 has an α-type two-cylinder configuration and is used as a refrigerator, and includes a crank chamber 2, a first cylinder 3 and a second cylinder 4 protruding from the crank chamber 2. The axes of the first cylinder 3 and the second cylinder 4 are perpendicular to each other. A piston 5 is inserted into the first cylinder 3 to constitute a compressor. A displacer 6 is inserted into the second cylinder 4 to constitute an expander. The compression space 7 in the first cylinder 3 and the expansion space 8 in the second cylinder 4 are communicated with each other by a gas pipe 9. The space in the compression space 7, the expansion space 8, and the gas pipe 9 is collectively referred to as “working space”. In the gas pipeline 9, a radiator 10 is provided near the first cylinder 3, and a regenerator 11 is provided near the second cylinder 4. The crank chamber 2 is provided with a crank disk 12 that is rotated by a power source (not shown) such as an electric motor (not shown). The piston 5 is connected to the crank disk 12 via the connecting rod 13, and the displacer 6 is connected to the connecting rod 14. Are connected to each other.

  When the crank disk 12 rotates, the piston 5 reciprocates within the first cylinder 3 and the displacer 6 reciprocates within the second cylinder 4 with a predetermined phase difference. As a result, the gas moves between the compression space 7 and the expansion space 8.

  The Stirling cycle apparatus 1A develops the operation according to the PV diagram of FIG. FIG. 4 shows a known thermodynamic cycle called a reverse Stirling cycle. In the compression process (1 → 2), the regenerator 11 and the expansion space 8 communicating with the compression space 7 become high pressure. In the expansion process (3 → 4) from the isobaric process (2 → 3), the space communicating from the expansion space 8 becomes a low pressure, and the cycle is restarted through the isovolumetric process (4 → 1).

  The gas in the compression space 7 whose pressure has increased in the compression process (1 → 2) and dissipated the heat in the radiator 10 transmits the heat to the regenerator 11 in the isovolumetric process (2 → 3), and then to the expansion space 8. Head to. The gas in the expansion space 8 becomes a low pressure during the expansion process (3 → 4), absorbs heat inside the second cylinder 4, and cools the portion surrounding the expansion space 8. This portion of the second cylinder 4 functions as an endothermic head (endothermic member) 4a, and the Stirling cycle device 1A can be used for use as a refrigerator by taking out cold heat from the endothermic head 4a. The gas in the expansion space 8 is drawn back to the compression space 7 side in an isovolumetric process (4 → 1), and exchanges heat with the regenerator 11 in the process.

  Next, the pressure accumulation space that is a feature of the present invention will be described. In the second cylinder 4 on the expansion space 8 side, a pressure accumulation space 15 is formed at an end portion facing the expansion space 8. The pressure accumulating space 15 is formed with a gas inflow port 16 composed of one through hole and a gas jet port 17 composed of a plurality of small diameter through holes facing the expansion space 8. A one-way valve 18 that prevents the gas in the pressure accumulation space 15 from flowing out is disposed inside the gas inlet 16. The one-way valve 18 is configured by fixing one end of a thin metal plate material (for example, phosphor bronze) to the inner wall of the pressure accumulating space 15 with a fastening member such as a screw or a rivet.

  FIG. 2 is a partially enlarged cross-sectional view of the Stirling cycle device around the endothermic head showing the gas behavior in the compression process. In the compression process, the expansion space 8 becomes a high pressure. Since this pressure is higher than the pressure in the pressure accumulation space 15, the gas pushes the one-way valve 18 through the gas inlet 16 and flows into the pressure accumulation space 15. At this time, a small amount of gas also flows from the gas outlet 17 into the pressure accumulation space 15. As described above, the pressure in the pressure accumulating space 15 also increases in accordance with the pressure increase in the expansion space 8 during the compression process.

  FIG. 3 is a partially enlarged cross-sectional view of the Stirling cycle device around the endothermic head showing the behavior of the gas in the expansion process. In the expansion process, the expansion space 8 becomes a low pressure, and the pressure in the pressure accumulation space 15 becomes a high pressure. Since there is a one-way valve 18 at the gas inlet 16, no gas flows out from here. Since the gas jet port 17 has a small diameter, the flow resistance is large, and no gas is jetted through the gas jet port 17 until the pressure difference between the expansion space 8 and the pressure accumulation space 15 reaches a certain level.

  When the pressure difference between the expansion space 8 and the pressure accumulation space 15 reaches a certain level, the gas in the pressure accumulation space 15 is ejected from the gas outlet 17. The ejection continues until the pressure difference between the expansion space 8 and the pressure accumulation space 15 becomes lower than the flow path resistance of the gas ejection port 17. During the ejection, the gas forms a jet in the expansion space 8, uniformizes the temperature of the gas in the expansion space 8, and promotes heat transfer between the gas and the heat absorbing head 4 a. Since heat exchange in the expansion process is thus promoted, the cold heat generated in the expansion space 8 can be efficiently taken out from the heat absorbing head 4a. The gas received in the pressure accumulating space 15 when the pressure in the expansion space 8 is higher is ejected into the expansion space 8 when the pressure in the expansion space 8 becomes lower. Becomes stronger, the gas in the expansion space 8 can be effectively disturbed, and higher engine efficiency can be obtained.

  The first embodiment is an application example to a two-cylinder Stirling cycle apparatus called α-type, but a similar accumulator space has a single-cylinder Stirling cycle apparatus called β-type or a γ-type two-cylinder. It can also be provided in a Stirling cycle apparatus having a configuration. That is, the configuration of the first embodiment can be used regardless of the type of the Stirling cycle apparatus. In the first embodiment, the pressure accumulation space is provided in the second cylinder on the heat absorption side. However, even if the same pressure accumulation space is provided in the first cylinder on the heat dissipation side, the heat transfer of the gas near the heat radiation head (heat radiation member) is promoted. can do. Furthermore, the engine efficiency can be further improved by attaching to both the heat absorbing head side and the heat radiating head side. Furthermore, in this example, although it used for the Stirling cycle apparatus of a refrigerator, the same effect is acquired also with the Stirling cycle apparatus of a motor.

  A second embodiment of the present invention will be described with reference to FIGS. FIG. 5 is a partially enlarged sectional view of the Stirling cycle apparatus according to the second embodiment, and FIG. 6 is a partially enlarged sectional view of the Stirling cycle apparatus in a state different from FIG.

  In the second embodiment, the structure of the cylinder is changed from that of the first embodiment. That is, the cylinder of the second embodiment has a pressure difference between the pressure accumulation space 15 and the expansion space 8 outside the gas outlet 17 (when the pressure accumulation space 15 has a higher pressure and the expansion space 8 has a lower pressure). A one-way valve 19 that opens when the pressure difference becomes equal to or greater than a predetermined value is arranged. The one-way valve 19 has the same structure as the one-way valve 18, but the opening direction is different.

  Even if the expansion space 8 becomes low pressure during the expansion process, and the pressure in the pressure accumulation space 15 becomes high compared to that, the one-way valve 19 does not open until the pressure difference reaches a predetermined value. Only when the pressure difference reaches a predetermined value, the one-way valve 19 is opened, and the gas in the pressure accumulating space 15 is ejected from the gas ejection port 17, so that the force of the ejected gas increases and the force for generating the jet becomes stronger. High engine efficiency can be obtained. Further, since gas leakage from the gas outlet 17 does not become a problem, the diameter of the gas outlet 17 can be increased, the jet flow rate can be increased, and the heat transfer rate can be greatly improved.

  A third embodiment of the present invention will be described with reference to FIGS. FIG. 7 is a cross-sectional view of the Stirling cycle apparatus according to the third embodiment, and FIG. 8 is a plan view of a cylinder jet mechanism portion of the Stirling cycle apparatus.

  The Stirling cycle apparatus 1B has a β-type cylinder configuration and is used as a refrigerator. The Stirling cycle apparatus 1B is a free piston type, and the first and second cylinders 30 and 31 form the center of assembly. The axes of the first and second cylinders 30 and 31 are aligned on the same straight line. A piston 32 is inserted into the first cylinder 30, and a displacer 33 is inserted into the second cylinder 31. The piston 32 and the displacer 33 reciprocate without contacting the inner walls of the first and second cylinders 30 and 31 by the mechanism of the gas bearing during the operation of the Stirling cycle apparatus 1B. The piston 32 and the displacer 33 move with a predetermined phase difference.

  A cup-shaped magnet holder 34 is provided at one end of the piston 32. A displacer shaft 35 protrudes from one end of the displacer 33. The displacer shaft 35 penetrates the piston 32 and the magnet holder 34 so as to be slidable in the axial direction, and protrudes into the back pressure space.

  The first cylinder 30 holds the linear motor 40 outside the portion corresponding to the operation area of the piston 32. The linear motor 40 is inserted in an annular space between the outer yoke 42 and the inner yoke 43, an outer yoke 42 provided with a coil 41, an inner yoke 43 provided so as to be in contact with the outer peripheral surface of the first cylinder 30. A ring-shaped magnet 44, a tubular body 45 surrounding the outer yoke 42, an outer yoke 42, an inner yoke 43, and synthetic resin end brackets 46 and 47 for holding the tubular body 45 in a predetermined positional relationship are provided. The magnet 44 is fixed to the magnet holder 34.

  The central portion of the spring 50 is fixed to the hub portion of the magnet holder 34. The center portion of the spring 51 is fixed to the displacer shaft 35. The outer peripheral portions of the springs 50 and 51 are fixed to the end bracket 47. A spacer 52 is disposed between the outer peripheries of the springs 50 and 51, whereby the springs 50 and 51 maintain a certain distance. The springs 50 and 51 are obtained by making a spiral cut into a disk-shaped material, and have the role of causing the displacer 33 to resonate with a predetermined phase difference (65 ° to 90 ° phase difference) with respect to the piston 32. Fulfill.

  A high temperature side heat transfer head (heat radiating member) 60 and a low temperature side heat transfer head (heat absorbing member) 61 are arranged outside the portion of the second cylinder 31 corresponding to the operating region of the displacer 33. The high temperature side heat transfer head 60, the low temperature side heat transfer head 61, and the regenerator tube 68 described later constitute a part of the outer shell of the Stirling cycle apparatus 1B.

  The high temperature side heat transfer head 60 has a ring shape, and the low temperature side heat transfer head 61 has a cap shape, both of which are made of metal having good heat conductivity such as copper or copper alloy. A ring-shaped high-temperature side internal heat exchanger 62 is mounted on the inner peripheral surface of the high-temperature side heat transfer head 60, and a ring-shaped low-temperature-side internal heat exchanger 63 is also mounted on the inner peripheral surface of the low-temperature side heat transfer head 61. Installed. Each of the high temperature side internal heat exchanger 62 and the low temperature side internal heat exchanger 63 has air permeability, and transfers the heat of the gas passing through the inside to the high temperature side heat transfer head 60 and the low temperature side heat transfer head 61. The high temperature side internal heat exchanger 62 and the low temperature side internal heat exchanger 63 are formed by corrugating a thin plate made of copper or copper alloy into a ring shape.

  The high temperature side heat transfer head 60 and the low temperature side heat transfer head 61 are thus supported outside the second cylinder 31 with the high temperature side internal heat exchanger 62 and the low temperature side internal heat exchanger 63 interposed therebetween. The first cylinder 30 and the pressure vessel 70 are connected to the high temperature side heat transfer head 60. The pressure vessel 70 encloses the linear motor 40, the first cylinder 30, and the piston 32. A space on the outer peripheral side of the first cylinder 30 inside the pressure vessel 70 is a back pressure space 71.

  An annular space surrounded by the high temperature side heat transfer head 60, the first and second cylinders 30 and 31, the piston 32, the displacer 33, the displacer shaft 35, and the high temperature side internal heat exchanger 62 is a compression space 65. A space surrounded by the low temperature side heat transfer head 61, the second cylinder 31, the displacer 33, and the low temperature side internal heat exchanger 63 becomes an expansion space 66.

  A regenerator 67 is disposed between the high temperature side internal heat exchanger 62 and the low temperature side internal heat exchanger 63 outside the second cylinder 31 that houses the displacer 33. The regenerator 67 is obtained by winding a resin film into a cylindrical shape, and a plurality of minute protrusions are scattered on one surface of the film to form gaps between the films at the height of the protrusions. Yes. A regenerator tube 68 wraps the outside of the regenerator 67 and forms an airtight passage between the heat transfer heads 60 and 61. The regenerator tube 68 can be formed of stainless steel, for example. Both ends of the regenerator tube 68 are connected to the inner surfaces of the high temperature side heat transfer head 60 and the low temperature side heat transfer head 61, and the high temperature side heat transfer head 60 and the low temperature side heat transfer head 61 are connected by the regenerator tube 68.

  The interior of the second cylinder 31 is a pressure accumulation space 80. A gas inlet 81, a one-way valve 82, and a gas outlet 83 are provided on the pressure accumulating space 80 on the side facing the expansion space 66. The structure of the gas inlet 81, the one-way valve 82, and the gas outlet 83 is the same as that of the gas inlet 16, the one-way valve 18, and the gas outlet 17 of the first embodiment. Similarly to the case of the first embodiment, the space occupied by the high temperature side heat exchanger 62, the space occupied by the low temperature side heat exchanger 63, the compression space 65, the expansion space 66, and the space occupied by the regenerator 67 are “ This is collectively referred to as “operating space”.

  The Stirling cycle apparatus 1B operates as follows. When an alternating current is supplied to the coil 41 of the linear motor 40, an alternating magnetic field penetrating the magnet 44 is generated between the inner yoke 43 and the outer yoke 42, and the magnet 44 reciprocates by receiving an electromagnetic force in the axial direction. The piston system is made smooth by supplying electric power having a frequency substantially equal to the resonance frequency determined by the total mass of the piston system (piston 32, magnet holder 34, magnet 44, and spring 50) and the spring constant of the spring 50. Start a sinusoidal reciprocating motion.

  In the displacer system (the displacer 33, the displacer shaft 35, and the spring 51), the resonance frequency determined by the total mass and the spring constant of the spring 51 is set to resonate with the drive frequency of the piston 32.

  Due to the reciprocating motion of the piston 32, the working spaces 62, 63, 65, 66 and 67 cause pressure changes such as compression and expansion. The displacer 33 also reciprocates in synchronization with the drive frequency of the piston 32 by the thrust resulting from this pressure change. At this time, a predetermined phase difference determined by the difference between the driving frequency of the piston 32 and the resonance frequency of the displacer system occurs between the reciprocating motion of the displacer 33 and the reciprocating motion of the piston 32.

  Due to the movement of the displacer 33, a reverse Stirling cycle is formed between the compression space 65 and the expansion space 66.

  The gas that moves between the compression space 65 and the expansion space 66 during operation passes through the high temperature side internal heat exchanger 62 and the low temperature side internal heat exchanger 63, and converts the heat of the gas into the high temperature side internal heat exchanger 62. Then, it is transmitted to the high temperature side heat transfer head 60 and the low temperature side heat transfer head 61 through the low temperature side internal heat exchanger 63. Since the gas from the compression space 65 toward the expansion space 66 is at a high temperature, the high temperature side heat transfer head 60 is heated, and the high temperature side heat transfer head 60 becomes a heat dissipation head. Since the gas from the expansion space 66 toward the compression space 65 is at a low temperature, the low temperature side heat transfer head 61 is cooled, and the low temperature side heat transfer head 61 becomes a heat absorption head. By radiating heat with the high temperature side heat transfer head 60 and absorbing heat with the low temperature side heat transfer head 61, the Stirling cycle device 1B functions as a refrigeration engine.

  The regenerator 67 functions to pass gas so that the sensible heat due to the gas temperature in the compression space 65 and the expansion space 66 is not transmitted to the counterpart space.

  The high temperature gas that has entered the regenerator 67 from the compression space 65 through the high temperature side internal heat exchanger 62 gives the sensible heat to the regenerator 67 when passing through the regenerator 67, and the low temperature side in a state where the temperature has decreased. It flows into the expansion space 66 through the internal heat exchanger 63. After the low temperature side internal heat exchanger 63 is cooled from the expansion space 66, the low temperature gas that has entered the regenerator 67 recovers sensible heat from the regenerator 67 when it passes through the regenerator 67, and the temperature has risen. Then, it flows into the compression space 65 through the high temperature side heat exchanger 62.

  In the Stirling cycle apparatus 1B, all the spaces of the compression space 65, the regenerator 67, the expansion space 66, the high temperature side and the low temperature side internal heat exchangers 62, 63 become high pressure during the compression process. Since this pressure is higher than the pressure in the pressure accumulating space 80, the gas flows from the gas inlet 81 into the pressure accumulating space 80 by pushing the one-way valve 82 open. FIG. 8 shows a gas inflow / outflow portion of the jet mechanism of the second cylinder 31. A gas inlet 81 and a gas jet 83 are arranged on the end face of the second cylinder 31 as shown in the figure. When the expansion process is started, all of the compression space 65, the regenerator 67, the expansion space 66, the high temperature side and low temperature side internal heat exchangers 62 and 63 become low pressure, and the pressure in the pressure accumulation space 80 becomes high compared to it. . Since the gas jet 83 has a small diameter, the flow resistance is large, and no gas is jetted through the gas jet 83 until the pressure difference between the expansion space 66 and the pressure accumulation space 80 reaches a certain level.

  When the pressure difference between the expansion space 66 and the pressure accumulation space 80 reaches a certain level, the gas in the pressure accumulation space 80 is ejected from the gas outlet 83. The ejection continues until the pressure difference between the expansion space 66 and the pressure accumulation space 80 becomes lower than the flow path resistance of the gas ejection port 83. During the ejection, the gas forms a jet in the expansion space 66, equalizes the temperature of the gas in the expansion space 66, and promotes heat transfer between the gas and the low-temperature side heat transfer head 61. Since heat exchange in the expansion process is thus promoted, the cold generated in the expansion space 66 can be efficiently taken out from the low temperature side heat transfer head 61.

  The gas received in the pressure accumulating space 80 when the pressure in the working space is high during the compression process is ejected into the expansion space 66 when the pressure in the working space becomes low during the expansion process, so the momentum of the gas blown out is strong. Thus, the gas in the expansion space 66 can be effectively disturbed, and higher engine efficiency can be obtained. Further, when the one-way valve 19 of the second embodiment is combined with the gas outlet 83, the momentum of the gas to be ejected is further increased, and higher efficiency can be obtained.

  A fourth embodiment of the present invention will be described with reference to FIG. In the fourth embodiment, the structure of the gas jet port is changed from that of the third embodiment. In other words, the gas jet port 90 is extended in a nozzle shape, is close to the heat absorbing surface of the low-temperature side heat transfer head 61, and is further angled so as to be substantially perpendicular to the heat absorbing surface. With this structure, the jet is realized by the same operation as in the third embodiment, and since it can be reliably applied to the heat transfer head surface, not only the gas stirring in the expansion space but also the gas in the vicinity of the heat transfer head surface Since the heat transfer rate is promoted by direct movement, the cold generated in the expansion space 66 can be efficiently taken out from the low temperature side heat transfer head 61.

  As mentioned above, although embodiment was demonstrated with the refrigerator, this technique is not restricted to a refrigerator.

  The present invention can be used for all Stirling cycle apparatuses.

Sectional drawing of the Stirling cycle apparatus which concerns on 1st Embodiment Partial enlarged sectional view of the Stirling cycle device A partially enlarged cross-sectional view of the Stirling cycle device in a state different from FIG. PV diagram of reverse Stirling cycle Partial enlarged sectional view of the Stirling cycle apparatus according to the second embodiment A partially enlarged sectional view of the Stirling cycle device in a state different from FIG. Sectional drawing of the Stirling cycle apparatus which concerns on 3rd Embodiment Plan view of the cylinder jet mechanism of the Stirling cycle device Partial enlarged sectional view of the Stirling cycle apparatus according to the fourth embodiment

Explanation of symbols

1A, 1B Stirling cycle device 2 Crank chamber 3, 30 First cylinder 4, 31 Second cylinder 4a Heat absorption head (heat absorption member)
5, 32 Piston 6, 33 Displacer 7, 65 Compression space 8, 66 Expansion space 9 Gas conduit 10 Radiator 11, 67 Regenerator 15, 80 Pressure accumulating space 16, 81 Gas inlet 17, 83 Gas outlet 18, 19 , 82 One-way valve 60 High temperature side heat transfer head (heat radiating member)
61 Low temperature side heat transfer head (heat absorption member)
90 Nozzle-shaped gas jet

Claims (6)

  The piston and the displacer are reciprocated with a phase difference from each other by a power source in the cylinder, and the resulting gas flow through the regenerator absorbs heat in the expansion space facing one end face of the displacer, A Stirling cycle apparatus for radiating heat in a compression space facing an end face of the Stirling cycle apparatus, wherein the cylinder is provided with a jet mechanism for jetting gas into the expansion space or the compression space.   The jet mechanism has a pressure accumulation space having a gas inlet and a gas outlet opening to the expansion space or the compression space, and the pressure accumulation space has a higher pressure in the expansion space or the compression space. 2. The Stirling cycle apparatus according to claim 1, wherein the Stirling cycle apparatus according to claim 1, wherein gas is received through the gas inflow port, and gas is ejected through the gas ejection port when the pressure in the expansion space or the compression space becomes lower.   A heat-absorbing member provided in contact with the inner surface of the expansion space, or a heat-dissipation member provided in contact with the inner surface of the compression space; and the gas jet port projecting toward the inner surface of the heat-absorbing member or heat-dissipation member The Stirling cycle apparatus according to claim 1, wherein the Stirling cycle apparatus has a nozzle shape.   The Stirling cycle apparatus according to claim 3, wherein the gas outlet is disposed so that a jet gas flow is substantially perpendicular to an inner surface of the heat absorbing member or the heat radiating member.   The Stirling cycle device according to any one of claims 1 to 4, wherein a one-way valve for preventing gas from flowing out of the pressure accumulation space is disposed at the gas inlet.   The one-way valve that opens when a pressure difference between the pressure accumulation space and the expansion space or the compression space becomes a predetermined value or more is disposed at the gas ejection port. The Stirling cycle apparatus of any one of these.

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