JP2006145076A - Heat radiation system and stirling refrigerator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat radiation system and a Stirling refrigerator capable of reducing the generation of noise and vibration, and preventing piping from being damaged. <P>SOLUTION: This heat radiation system comprises a first high temperature-side circulation circuit including a high temperature-side evaporator 5 mounted around a heat radiating portion 2 of a Stirling freezer 4, and a high temperature-side condenser 7, and a second high temperature-side circulation circuit as a forced-circulation circuit by a circulation pump 6. A refrigerant flow channel from the high temperature-side evaporator 5 to the circulation pump 6 in the second high temperature-side circulation circuit has a flow channel portion 320 of a suction tank 32 from the neighborhood of a height position of the high temperature-side evaporator 5 to the neighborhood of a height position of the circulation pump 6, and pipes 2C, 2D connecting the flow channel portion 320 and the circulation pump 6 and the high temperature-side evaporator 5, a projecting portion 321 is formed in a state of projecting to an upper side of the flow channel portion 320 from an upper end portion of the flow channel portion 320, and at least a flow channel area of the flow channel portion 320 is larger than an average flow channel area of the pipes 2E, 2F and a dew-proofing pipe 9. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a heat dissipation system and a Stirling Refrigerator / Freezer, and more particularly, to a heat dissipation system and a Stirling cooler in which the occurrence of cavitation in refrigerant piping is suppressed.

  As what applied the heat exchange by a reverse Stirling cycle to a refrigerator, what was described in Unexamined-Japanese-Patent No. 2003-50073 (conventional example 1) etc. are mentioned, for example.

In Conventional Example 1, the high temperature part for radiating the compression heat of the working gas due to the reverse Stirling cycle to the outside, the low temperature part for absorbing the expansion heat of the working gas due to the reverse Stirling cycle from the outside, and the heat at the low temperature part A low-temperature side circulation circuit composed of a closed circuit in which a low-temperature side condenser and a plurality of low-temperature side evaporators connected to form a thermosiphon are connected to each other, A Stirling refrigeration system is disclosed that is enclosed in a side circulation circuit. Here, the heat in the high temperature part is radiated by the high temperature side heat exchange cycle (heat radiation system). The high temperature side heat exchange cycle includes a high temperature side evaporator and a high temperature side condenser connected by piping, and heat is conveyed and released by the thermosiphon principle.
JP 2003-50073 A

  However, the above heat dissipation system has the following problems.

  In the heat dissipation system, in addition to the thermosiphon circuit described above, a forced circulation circuit that includes a circulation pump and is supplied with a liquefied refrigerant from a high-temperature side evaporator may be formed. The heat of the refrigerant flowing in the forced circulation circuit is used, for example, to prevent dew generation in a refrigerator.

  Here, since a relatively high temperature refrigerant is supplied from the high temperature side evaporator to the piping of the forced circulation circuit, bubbles are likely to be generated in the refrigerant flowing through the piping (the cavitation is likely to occur). Yes. After the cavitation occurs, the pressure in the portion increases again, and the generated bubbles disappear. At this time, there is a problem that noise or vibration may be generated or the pipe may be damaged due to an impact (water hammer) resulting from a large space fluctuation.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a heat dissipation system and a Stirling cooler in which noise, vibrations, and damage to piping are suppressed. It is to provide.

  In one aspect, the heat dissipation system according to the present invention is provided around an heat source, and includes an evaporator that evaporates an internal refrigerant, and a condenser that receives the evaporated refrigerant and condenses the refrigerant, and is condensed. A first circulation circuit for returning the refrigerant into the evaporator; a refrigerant flow path connected to the lower part of the evaporator; and a circulation pump provided below the evaporator of the refrigerant flow path, A refrigerant circuit from the evaporator to the circulation pump in the second circulation circuit, from the vicinity of the height where the evaporator is located to the vicinity where the circulation pump is located And a projecting portion that projects from the upper end of the first portion to the upper side of the first portion. The flow area of at least the first part is the second circulation time Greater than the average flow area downstream of the circulation pump in the.

  Here, the average flow path area on the downstream side of the circulation pump means the average value of the area of the refrigerant flow path from the outlet (discharge part) of the circulation pump to the evaporator. Further, the flow passage area of only the first portion may be relatively large, or the flow passage area in all portions located upstream of the circulation pump including the first and second portions may be circulated. You may make it become larger than the average flow path area of the downstream rather than a pump.

  According to this configuration, by increasing at least the flow path area of the first portion, bubbles generated in the circulation circuit are likely to rise and easily accumulate in the protruding portion. Even if the bubbles disappear in the first portion, the water hammer is mitigated because the diameter of the pipe is large. As a result, noise, vibration, damage to piping, and the like due to water hammer are suppressed.

  Here, it is preferable that the protruding portion protrudes above the evaporator.

  Thereby, sufficient gas phase space can be secured. As a result, bubbles in the refrigerant flow path can be reduced.

  The flow path area of the first portion is preferably not less than 2 times and not more than 16 times the average flow path area on the downstream side of the circulation pump in the second circulation circuit.

  Thereby, the effect which suppresses the noise by a water hammer, the vibration, the damage of piping, etc. can be acquired stably, suppressing the space required for piping of the 1st part becoming large too much.

  In another aspect, the heat dissipation system according to the present invention is provided around the heat source, and includes an evaporator that evaporates the internal refrigerant, and a condenser that receives the evaporated refrigerant and condenses the refrigerant. A first circulation circuit for returning the refrigerant into the evaporator; a refrigerant flow path connected to the lower part of the evaporator; and a circulation pump provided below the evaporator of the refrigerant flow path, And a pulsation absorption pipe having a portion extending in the vertical direction and connected to the refrigerant flow path in the vicinity of the inlet and / or outlet of the circulation pump in the second circulation circuit.

  According to this structure, the pressure fluctuation accompanying the pulsation in a refrigerant flow path can be suppressed. As a result, noise, vibration, piping damage, and the like due to water hammer accompanying cavitation are suppressed.

  Here, it is preferable that the front-end | tip part of a pulsation absorption pipe protrudes above an evaporator.

  Thereby, a gas phase space can be secured stably at the tip of the pulsation absorbing pipe. As a result, the ability to absorb pulsation is improved.

  A heat insulating means may be provided around the pulsation absorbing pipe.

  Thereby, the temperature in a pulsation absorption pipe becomes high, the volume of the gaseous-phase space of the pulsation absorption pipe front-end | tip part becomes large, and a pulsation absorption capability improves.

  A piezoelectric pump may be used as the circulation pump. By using the piezoelectric pump, pulsation is generated, and bubbles are easily generated in the refrigerant. According to the present invention, there is an effect of suppressing water hammer due to the generation and disappearance of the bubbles.

  The Stirling refrigerator according to the present invention includes the above-described heat dissipation system configured with the high temperature part of the Stirling refrigerator as a heat source.

  In the heat dissipation system described above, water hammer in the refrigerant pipe is suppressed. Therefore, a Stirling cooler in which generation of noise and the like is suppressed is provided.

  ADVANTAGE OF THE INVENTION According to this invention, the Stirling refrigerator provided with the thermal radiation system and this system with which the noise, the vibration, and the damage to piping were suppressed by the water hammer are provided.

  Embodiments of a heat dissipation system and a Stirling cooler according to the present invention will be described below with reference to FIGS. 1 to 3.

  In the present specification, the “cooling box” is a concept including all of “refrigerator”, “freezer”, and “freezer refrigerator”.

  Further, in the present embodiment, a Stirling cooler as a Stirling engine mounted device provided with a Stirling refrigerator will be described, but the Stirling engine mounted device provided with the heat dissipation system according to the present invention is limited to the Stirling cooler. It is not something. The Stirling engine is also used as a generator, for example.

  FIG. 1 is a piping system diagram of a Stirling cooler according to one embodiment of the present invention.

  As shown in FIG. 1, the Stirling refrigerator 1 according to the present embodiment includes a Stirling refrigerator 4 (Stirling engine) having a heat radiating unit 2 and a heat absorbing unit 3, and a high-temperature side evaporator attached to the heat radiating unit 2. 5, a first high temperature side circulation circuit (first circulation circuit) including a high temperature side condenser 7 and pipes 2A, 2B, a high temperature side evaporator 5, a circulation pump 6, a dew condensation prevention pipe 9, pipes 2C, 2D, 2E, 2F and the 2nd high temperature side circulation circuit (second circulation circuit) containing the suction tank 32, and the low temperature side circulation circuit containing the low temperature side condenser 10, the low temperature side evaporator 11 and the pipes 3A and 3B attached to the heat absorption part 3 With. The first high temperature side circulation circuit cools the heat radiating part 2 of the Stirling refrigerator 4, and the second high temperature side circulation circuit supplies heat to the dew condensation prevention pipe 9. In addition, the low-temperature side circulation circuit performs heat exchange between the air in the refrigerator and the heat absorption unit 3 of the Stirling refrigerator 4.

Water (H ₂ O) or the like is sealed as a refrigerant in the first and second high temperature side circulation circuits. The refrigerant evaporated in the high temperature side evaporator 5 reaches the high temperature side condenser 7 via the pipe 2A (high temperature side conduit) (broken line arrow in FIG. 1). The refrigerant is condensed by heat exchange with the outside air in the high temperature side condenser 7. In order to promote this heat exchange, a fan 8 that generates an air flow in the vicinity of the high-temperature side condenser 7 is provided. The condensed refrigerant returns to the high temperature side evaporator 5 through the pipe 2B (high temperature side return pipe). In the first high temperature side circulation circuit, the high temperature side condenser 7 is heated at a high temperature so that the heat generated in the heat radiating unit 2 can be transferred using the natural circulation caused by the evaporation and condensation of the refrigerant. It is arranged above the side evaporator 5. In order to adjust the boiling point of the refrigerant, the pressure in the circulation circuit system is adjusted (substantially reduced in vacuum).

  On the other hand, a pipe 2 </ b> C is connected to the lower part of the high temperature side evaporator 5. Liquid phase refrigerant flows from the high temperature side evaporator 5 into the pipe 2C. The refrigerant flowing into the pipe 2C reaches the circulation pump 6 provided below the Stirling refrigerator 4 through the suction tank 32 and the pipe 2D. The refrigerant discharged from the circulation pump 6 is sent to the dew prevention pipe 9 through the pipe 2E. Here, the refrigerant flowing in the dew condensation prevention pipe 9 is kept at a relatively high temperature by the heat given from the heat radiating unit 2 of the Stirling refrigerator 4. Therefore, the dew condensation prevention pipe 9 can be disposed on the front surface of the refrigerator to suppress dew condensation on the door portion or the like. The refrigerant that has flowed through the dew condensation prevention pipe 9 returns to the high temperature side evaporator 5 through the pipe 2F. Thus, forced circulation by the circulation pump 6 is performed in the second high temperature side circulation circuit. A pulsation absorbing pipe 33 is connected to the pipe 2E located near the outlet of the circulation pump 6.

  The suction tank 32 has a flow path portion 320 that extends in the vertical direction and connects the pipe 2C and the pipe 2D, and a protruding portion 321 that protrudes upward from the flow path portion 320. Here, the flow passage area of the suction tank 32 is larger than the flow passage areas of the pipes 2C, 2D, 2E, 2F and the dew prevention pipe 9.

  As described above, in the second high temperature side circulation circuit, in order to adjust the boiling point of the refrigerant, the pressure in the circulation circuit system is set low, and the inside of the refrigerant flow path from the evaporator 5 to the circulation pump 6 is set. It is considered that the flowing refrigerant is almost in the state of saturated liquid. Therefore, bubbles are generated in the refrigerant due to local pressure fluctuations, and when this returns to the liquid phase again, impact (water hammer) due to large volume fluctuations is brought about, causing noise, vibration, and piping damage. Is concerned.

  On the other hand, by providing the suction tank 32 having a large cross-sectional area as described above, the bubbles generated in the flow path portion 320 can be easily moved upward. The bubbles that have moved upward are stored in the protruding portion 321. Here, by projecting the upper end of the protruding portion 321 above the high-temperature side evaporator 5, the protruding portion 321 can be stably provided at the tip of the protruding portion 321 regardless of the liquid level of the refrigerant in the high-temperature side evaporator 5. Gas space can be secured.

  The axial cross-sectional shape of the suction tank 32 can be changed as appropriate, but when the cross-sectional shape is circular, the diameter is about 1.5 to 4 times the flow area of other pipes. It is preferable that For example, when the inner diameters of the pipes 2C, 2D, 2E, 2F and the dew prevention pipe 9 are about 6 mm, the preferable range of the inner diameter of the suction tank 32 is about 9 mm to 24 mm. In other words, the flow passage area of the suction tank 32 is preferably about 2 to 16 times the flow passage area of other pipes in the second high temperature side circulation circuit.

  Thereby, the effect which suppresses the noise by a water hammer, the vibration, the damage of piping, etc. can be acquired stably, suppressing that the space required for arrangement | positioning of the suction tank 32 becomes large too much.

  In the example shown in FIG. 1, only the flow passage area of the suction tank 32 is set to be relatively large, but the flow passage portion 320 of the suction tank 32 and the pipes 2C and 2D (on the upstream side of the circulation pump 6). The flow path area of the pipe (positioned pipe) may be set to be larger than the average flow path area of the pipes 2E and 2F and the dew prevention pipe 9 (pipe located on the downstream side of the circulation pump 6). For example, it is conceivable to use pipes having the same thickness as the suction tank 32 as the pipes 2C and 2D.

  The pulsation absorbing pipe 33 extends in the vertical direction. A gas space is formed at the tip of the pulsation absorption pipe 33, and the refrigerant in the pulsation absorption pipe 33 flows into the pipe 2E, or the refrigerant in the pipe 2E flows into the pulsation absorption pipe 33, so that the pipe 2E. Inner flow pulsations are reduced. Since the pulsation leads to the occurrence of cavitation due to local pressure fluctuations, the occurrence of cavitation is suppressed by providing the pulsation absorbing pipe 33.

  In the example shown in FIG. 1, the pulsation absorption pipe 33 is provided only on the downstream side (near the outlet) of the circulation pump 6, but the pulsation absorption pipe (not shown) is also provided on the upstream side (near the inlet) of the circulation pump 6. May be provided. Thereby, pulsation is also suppressed on the inlet side of the circulation pump 6. A plurality of pulsation absorbing pipes 33 may be connected to one or both of the vicinity of the outlet and the vicinity of the inlet of the circulation pump 6.

  As the circulation pump 6, typically, a piezoelectric pump using a piezoelectric element such as crystal or lithium niobate is used, but other types of pumps may be used.

  Carbon dioxide, hydrocarbons, and the like are enclosed as a refrigerant in a low-temperature side circulation circuit that performs heat exchange between the air in the refrigerator and the heat absorption unit 3 of the Stirling refrigerator 4. The refrigerant condensed in the low temperature side condenser 10 reaches the low temperature side evaporator 11 through the pipe 3A (low temperature side conduit). Heat exchange is performed by evaporating the refrigerant in the low temperature side evaporator 11. In order to promote this heat exchange, a fan 12 that generates an air flow in the vicinity of the low-temperature evaporator 11 is provided. After the heat exchange, the gasified refrigerant returns to the low temperature side condenser 10 through the pipe 3B (low temperature side return pipe). In the low-temperature side circulation circuit, the low-temperature side evaporator 11 is thus condensed on the low-temperature side so that the cold generated in the heat-absorbing unit 3 can be transmitted using the natural circulation caused by the evaporation and condensation of the refrigerant. It is arranged below the vessel 10. In order to adjust the boiling point of the refrigerant, the pressure in the circulation circuit system is adjusted (substantially reduced in vacuum).

  When the Stirling refrigerator 4 is operated, the heat generated in the heat radiating unit 2 of the refrigerator 4 is exchanged with air through the high temperature side condenser 7. On the other hand, the cold generated in the heat absorption part 3 of the Stirling refrigerator 4 is heat-exchanged with the air in the refrigerator through the low temperature side evaporator 11. The warmed airflow from the inside of the refrigerator is sent again to the vicinity of the low-temperature side evaporator 11 and repeatedly cooled.

  FIG. 2 is a diagram showing a second high temperature side circulation circuit in the Stirling refrigerator 1.

  Referring to FIG. 2, Stirling refrigerator 4 is provided in machine room 31. As shown in FIG. 2, the second high temperature side circulation circuit passes the refrigerant in the high temperature side evaporator 5 from the lower part of the high temperature side evaporator 5 through the pipe 2C, the suction tank 32, the pipe 2D, the circulation pump 6 and the pipe 2E. After being led to the dew condensation prevention pipe 9 and circulated through the entire front surface of the Stirling cooler main body 1A, it is returned from the upper part of the high temperature side evaporator 5 into the evaporator 5 through the pipe 2F. Here, the circulation pump 6 is installed below the high temperature side evaporator 5. Thereby, the pressure of the refrigerant | coolant which flows through the circulation pump 6 vicinity using the position head difference can be made high, and generation | occurrence | production of a cavitation can be suppressed.

  In the suction tank 32 and the pulsation absorbing pipe 33, liquid phase portions 32A and 33A and gas phase spaces 33A and 33B are formed, respectively. By projecting the tips of the suction tank 32 and the pulsation absorption pipe 33 above the high-temperature side evaporator 5, the gas phase spaces 32 </ b> B and 33 </ b> B are stably secured at the tips of the suction tank 32 and the pulsation absorption pipe 33. be able to. Thereby, the desired effect mentioned above can be acquired stably.

  Further, a heat insulating material (heat insulating means) may be provided around the pulsation absorbing pipe 33. For example, it can be considered that the pulsation absorbing pipe 33 is embedded in urethane or the like provided on the side surface or the back surface of the refrigerator main body 1A. Thereby, the temperature in the pulsation absorption pipe 33 is increased, the volume of the gas phase space 33B at the tip of the pulsation absorption pipe is increased, and the pulsation absorption capability is improved.

  The above contents are summarized as follows.

  The heat dissipating system according to the present embodiment is provided around the heat dissipating unit 2 (heat source) of the Stirling refrigerator 4, accepts the high-temperature side evaporator 5 that evaporates the internal refrigerant, and the evaporated refrigerant, and condenses the refrigerant. A high-temperature side condenser 7, a first high-temperature side circulation circuit for returning the condensed refrigerant into the high-temperature side evaporator 5, a refrigerant flow path including a pipe 2 </ b> C connected to the lower part of the high-temperature side evaporator 5, and Including a circulation pump 6 attached to the refrigerant flow path, and a second high temperature side circulation circuit for guiding the refrigerant to the dew condensation prevention pipe 9 (heat dissipating part) and then returning the refrigerant to the high temperature side evaporator 5. (2) In the high temperature side circulation circuit, the circulation pump 6 is arranged at a position lower than the high temperature side evaporator 5, and the refrigerant flow path from the high temperature side evaporator 5 to the circulation pump 6 in the second high temperature side circulation circuit is at a high temperature. Circulation pump from the vicinity of the height where the side evaporator 5 is located The flow path part 320 (first part) of the suction tank 32 reaching the vicinity of the height where the 6 is located, and the pipes 2C, 2D (second part) connecting the flow path part 320 to the circulation pump 6 and the high temperature side evaporator 5 ) And a protruding portion 321 that protrudes from the upper end portion of the flow path portion 320 to the upper side of the flow path portion 320 is provided, and at least the flow path area of the flow path portion 320 of the suction tank 32 is larger than that of the circulation pump 6. Is larger than the average flow path area of the pipes 2E and 2F and the dew condensation prevention pipe 9 which are the flow paths on the downstream side.

  In this configuration, since the flow path area of the flow path portion 320 of the suction tank 32 is relatively large, bubbles generated in the suction tank 32 are likely to rise. The raised bubbles are stored in the protruding portion 321. Further, even if the bubbles once generated in the flow path portion 320 disappear, the water hammer caused by the volume change is relieved because the diameter of the suction tank 32 is large. As a result, noise, vibration, damage to piping, and the like due to water hammer are suppressed.

  The heat dissipation system includes a pulsation absorbing pipe 33 that is connected to a pipe 2E (refrigerant flow path) near the outlet of the circulation pump 6 in the second high temperature side circulation circuit and has a portion extending in the vertical direction.

  Thereby, the pressure fluctuation accompanying the pulsation in the pipe 2E located in the vicinity of the exit of the circulation pump 6 can be suppressed. Since this location is a location where the frequency of water hammer due to pressure fluctuation is relatively high, the provision of the pulsation absorbing pipe 33 here suppresses noise, vibration, damage to piping, etc. due to water hammer. The

  In the heat dissipation system described above, water hammer in the refrigerant flow path is suppressed. Therefore, a Stirling cooler in which noise, vibration and the like are suppressed is provided.

  Next, an example of the structure of the Stirling refrigerator 4 and its operation will be described with reference to FIG.

  As shown in FIG. 3, the Stirling refrigerator 4 of the present embodiment is a free piston type Stirling engine, and includes a casing 30, a cylinder 13 assembled to the casing 30, and a reciprocating motion in the cylinder 13. Piston 14 and displacer 15, regenerator 16, working space 17 including a compression space 17 </ b> A and an expansion space 17 </ b> B, a heat radiating portion 2, a heat absorbing portion 3, a linear motor 23 as a piston driving means, and a piston spring 24, a displacer spring 25, a displacer rod 26, and a back pressure space 27.

  In the example of FIG. 3, the outer shell (outer wall) of the Stirling refrigerator 4 is not formed of a single container, but is positioned on the back pressure space 27 side and the casing 30 (vessel portion), and on the working space 17 side. The heat radiating part 2, the tube 18A and the heat absorbing part 3 are mainly configured. The casing 30 defines a back pressure space 27. Various parts including the cylinder 13, the linear motor 23, the piston spring 24, and the displacer spring 25 are assembled to the casing 30. The outer shell is filled with a working medium such as helium gas, hydrogen gas, or nitrogen gas.

  The cylinder 13 has a substantially cylindrical shape, and receives therein a piston 14 and a displacer 15 as a free piston so as to be capable of reciprocating. In the cylinder 13, the piston 14 and the displacer 15 are coaxially spaced apart, and the piston 14 and the displacer 15 divide the working space 17 in the cylinder 13 into a compression space 17 </ b> A and an expansion space 17 </ b> B. More specifically, the working space 17 is a space located closer to the displacer 15 than the end face of the piston 14 on the displacer 15 side, and a compression space 17A is formed between the piston 14 and the displacer 15, and the displacer 15 and the heat absorbing portion. 3, an expansion space 17 </ b> B is formed. The compression space 17 </ b> A is mainly surrounded by the heat radiating part 2, and the expansion space 17 </ b> B is mainly surrounded by the heat absorption part 3.

  Between the compression space 17A and the expansion space 17B, a regenerator 16 in which a film is wound with a predetermined gap on the inner peripheral surface of the tube 18A is disposed. The compression space 17A and the expansion space 17B communicate with each other. Thereby, a closed circuit is formed in the Stirling refrigerator 4. The working medium sealed in the closed circuit flows in accordance with the operations of the piston 14 and the displacer 15, thereby realizing a reverse Stirling cycle described later.

  A linear motor 23 is disposed in the back pressure space 27 located outside the cylinder 13. The linear motor 23 includes an inner yoke 20, a movable magnet portion 21, and an outer yoke 22, and the piston 14 is driven in the axial direction of the cylinder 13 by the linear motor 23.

  One end of the piston 14 is connected to a piston spring 24 constituted by a leaf spring or the like. The piston spring 24 functions as an elastic force applying means for applying an elastic force to the piston 14. By applying an elastic force to the piston spring 24, the piston 14 can be reciprocated in the cylinder 13 more stably and periodically. One end of the displacer 15 is connected to a displacer spring 25 via a displacer rod 26. The displacer rod 26 is disposed through the piston 14, and the displacer spring 25 is constituted by a leaf spring or the like. The peripheral edge of the displacer spring 25 and the peripheral edge of the piston spring 24 are supported by a support member that extends from the linear motor 23 toward the back pressure space 27 of the piston 14 (hereinafter sometimes referred to as the rear).

  A back pressure space 27 surrounded by a casing 30 is disposed on the opposite side of the piston 14 from the displacer 15. The back pressure space 27 includes an outer peripheral region located around the piston 14 in the casing 30 and a rear region located closer to the piston spring 24 (rear side) than the piston 14 in the casing 30. There is also a working medium in the back pressure space 27.

  A heat exchanger 18 and a heat exchanger 19 are provided on the inner peripheral surfaces of the heat radiating unit 2 and the heat absorbing unit 3, respectively. The heat exchangers 18 and 19 perform heat exchange between the compression space 17A and the expansion space 17B and the heat radiating unit 2 and the heat absorbing unit 3, respectively.

  A balance mass 29 is attached to the rear side of the casing 30 via a leaf spring 28. The balance mass 29 is a mass member that absorbs vibration of the casing 30 that is generated when the piston 14 and the displacer 15 vibrate. Specifically, when the vibration is generated in the casing 30 due to the vibration of the piston 14 or the displacer 15, the balance mass 29 is vibrated so as to follow the vibration of the casing 30, whereby the Stirling refrigerator 4. Vibration is reduced.

  Next, the operation of the Stirling refrigerator 4 will be described.

  First, the linear motor 23 is actuated to drive the piston 14. The piston 14 driven by the linear motor 23 approaches the displacer 15 and compresses the working medium (working gas) in the compression space 17A.

  When the piston 14 approaches the displacer 15, the temperature of the working medium in the compression space 17 </ b> A rises, but heat generated in the compression space 17 </ b> A is released to the outside by the heat radiating unit 2. Therefore, the temperature of the working medium in the compression space 17A is maintained almost isothermal. That is, this process corresponds to an isothermal compression process in a reverse Stirling cycle.

  After the piston 14 approaches the displacer 15, the displacer 15 moves to the heat absorption unit 3 side. On the other hand, the working medium compressed in the compression space 17A by the piston 14 flows into the regenerator 16, and further flows into the expansion space 17B. At that time, the heat of the working medium is stored in the regenerator 16. That is, this process corresponds to an isovolumetric cooling process in a reverse Stirling cycle.

  The high-pressure working medium that has flowed into the expansion space 17B expands when the displacer 15 moves to the piston 14 side (rear side). As the displacer 15 moves rearward in this way, the center portion of the displacer spring 25 is also deformed so as to protrude rearward.

  As described above, when the working medium expands in the expansion space 17B, the temperature of the working medium in the expansion space 17B decreases, but external heat is transferred into the expansion space 17B by the heat absorbing unit 3, The inside of the expansion space 17B is kept almost isothermal. That is, this process corresponds to an isothermal expansion process of a reverse Stirling cycle.

  Thereafter, the displacer 15 starts to move away from the piston 14. Thereby, the working medium in the expansion space 17B passes through the regenerator 16 and returns to the compression space 17A side again. At this time, since the heat stored in the regenerator 16 is applied to the working medium, the working medium is heated. That is, this process corresponds to a constant volume heating process of a reverse Stirling cycle.

  By repeating this series of processes (isothermal compression process-isovolume cooling process-isothermal expansion process-isovolume heating process), an inverse Stirling cycle is configured. As a result, the endothermic part 3 gradually becomes low temperature and has a very low temperature. On the other hand, the heat radiating part 2 gradually becomes high temperature. As described above, the cold heat in the heat absorption unit 3 is supplied into the refrigerator through the low temperature side circulation circuit, and the heat in the heat dissipation unit 2 is released to the outside of the refrigerator through the first and second high temperature side circulation circuits. Is done.

  Although the embodiments of the present invention have been described above, the embodiments disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

It is a piping system diagram of a Stirling cooler according to one embodiment of the present invention. It is the figure which showed the 2nd high temperature side circulation circuit in the thermal radiation system which concerns on one embodiment of this invention. It is the sectional side view which showed the Stirling refrigerator in the Stirling refrigerator which concerns on one embodiment of this invention.

Explanation of symbols

  1 Stirling refrigerator, 2 heat dissipating section, 2A to 2F pipe (high temperature side circulation circuit), 3 heat absorption section, 3A, 3B pipe (low temperature side circulation circuit), 4 Stirling refrigerator, 5 high temperature side evaporator, 6 circulation pump, 7 High-temperature side condenser, 8 fan, 9 Dew prevention pipe, 10 Low-temperature side condenser, 11 Low-temperature side evaporator, 12 Fan, 13 Cylinder, 14 Piston, 15 Displacer, 16 Regenerator, 17 Working space, 17A Compression space, 17B expansion space, 18, 19 heat exchanger, 18A tube, 20 inner yoke, 21 movable magnet, 22 outer yoke, 23 linear motor, 24 piston spring, 25 displacer spring, 26 displacer rod, 27 back pressure space, 28 leaf spring 29 Balance mass, 30 Casing, 3 Machine room, 32 suction tank, 32A, 33A liquid phase portion, 32B, 33B vapor space, 33 pulsation absorber pipe, 320 channel portion, 321 protruding portions.

Claims (6)

A first circulation circuit that is provided around a heat source and includes an evaporator that evaporates an internal refrigerant and a condenser that receives the evaporated refrigerant and condenses the refrigerant, and returns the condensed refrigerant to the evaporator. Circuit,
A refrigerant flow path connected to a lower portion of the evaporator and a circulation pump provided below the evaporator in the refrigerant flow path, and a second circulation for guiding the refrigerant to a heat radiating portion and returning the refrigerant into the evaporator With circuit,
The refrigerant flow path from the evaporator to the circulation pump in the second circulation circuit has a first portion that reaches from the vicinity of the height where the evaporator is located to the height where the circulation pump is located, A first part and a second part connecting the circulation pump and the evaporator;
A protruding portion protruding from the upper end of the first portion to the upper side of the first portion;
A heat dissipation system in which at least the flow area of the first portion is larger than the average flow area on the downstream side of the circulation pump in the second circulation circuit.   The heat dissipation system according to claim 1, wherein the protruding portion protrudes upward from the evaporator. A first circulation circuit that is provided around a heat source and includes an evaporator that evaporates an internal refrigerant and a condenser that receives the evaporated refrigerant and condenses the refrigerant, and returns the condensed refrigerant to the evaporator. Circuit,
A refrigerant flow path connected to a lower portion of the evaporator and a circulation pump provided below the evaporator in the refrigerant flow path, and a second circulation for guiding the refrigerant to a heat radiating portion and returning the refrigerant into the evaporator Circuit,
A heat dissipation system comprising: a pulsation absorption pipe having a portion extending in a vertical direction, connected to the refrigerant flow path in the vicinity of the inlet and / or outlet of the circulation pump in the second circulation circuit.   The heat dissipating system according to claim 3, wherein a tip end portion of the pulsation absorbing pipe projects upward from the evaporator.   The heat dissipation system according to claim 3 or 4, further comprising heat insulating means around the pulsation absorbing pipe.   The Stirling refrigerator provided with the thermal radiation system in any one of Claims 1-5 comprised as the heat source the high temperature part of the Stirling refrigerator.

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