JPH06323657A - Refrigerator - Google Patents

Abstract

PURPOSE:To reduce the loss due to heat leakage as much as possible even if a refrigerating operation is interrupted. CONSTITUTION:A refrigerator supplies cold generated by a heat cycle having an expanding step of operating gas to be guided from a compressing space to an expanding space from a refrigeration output unit 8 to a refrigerating load 43, and comprises a heat pipe 37 connected to the unit 8 and the load 43 side to supply cold from the unit 8 to the refrigerating load 43 via operating liquid 40 at the time of refrigerating and to evaporate the liquid 40 at the time of interrupting the refrigerating to shut OFF heat between the unit 8 and the refrigerating load 43.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerating apparatus for extracting cold heat by using a cold storage type refrigerator such as a Stirling refrigerator.

[0002]

2. Description of the Related Art In the field of advanced technology such as the field of biotechnology and the field of electronic devices, there is an urgent need to develop an ultralow temperature preservation technique for various samples and various materials. In particular, cold storage type refrigerators such as Stirling refrigerators are attracting attention as means for realizing the above-mentioned ultra-low temperature, and are being widely used as freezers, freezers and the like for cooling various infrared sensors, superconducting devices and the like, biomedicals.

The operation principle of the two-piston Stirling refrigerator will be described with reference to FIG.

The Stirling refrigerator 1 has a gas flow path 5 in which a gas compressor 2 and an expander 3 are interposed, and a regenerator 4 is interposed therebetween.
A radiator 6 is provided on the gas compressor 2 side of the gas flow path 5 and a radiator 7 is provided on the inlet side of the regenerator 4, while a freezing take-out portion 8 is formed on the upper portion of the expander 3. Further, a crank mechanism portion 9 is arranged behind the gas compressor 2 and below the expander 3.

The gas compressor 2 compresses a working gas having a cryogenic boiling point such as helium according to a predetermined cycle and supplies the compressed working gas to the expander 3. The gas compressor 2 is a compression cylinder. A compression space 11 for compressing the working gas is formed inside the main body 10, and a compression piston 13 is slidably fitted in a compression cylinder 12 and the compression piston 13 reciprocates by the action of a crank mechanism section 9 described later. It is like this.

The expander 3 expands the compressed working gas supplied from the gas compressor 2 via the regenerator 4, and the expander 3 has an expansion cylinder 15 inside the expander body 14 in the vertical direction. The expansion piston 16 is slidably fitted in the expansion cylinder 15 in the vertical direction, and the freezing generation section 17 is formed inside the expansion machine 3 as an expansion space in which a low temperature is generated.

The regenerator 4 is formed in a cylindrical shape between the inner circumference of the expander body 14 and the outer circumference of the expansion cylinder 15, and is a compressed working gas supplied to the expander 3 via the gas flow path 5. On the other hand, when the working gas expanded and cooled in the freezing generation section 17 is returned to the gas compressor 2 while being cooled, the working gas is cooled to store the cold, and the material thereof is copper having a large specific heat. And stainless steel, and lead, etc., are used, and they are formed in a cylindrical shape having a large number of fine holes through which a working gas passes.

The gas flow path 5 is a pipe for connecting the gas compressor 2 and the expander 3 so that the compressed working gas uniformly passes through the regenerator 4 at the inlet side of the regenerator 4. The radiator 6 and the radiator 7 lower the compressed high-temperature working gas to near room temperature. The radiator 6 has a large number of disc-shaped fins standing outside the body of the compression cylinder body 10 to radiate heat. Bowl 7
Has a large number of circular fins standing on the outside of the body of the expander body 14. The freezing take-out unit 8 includes the freezing generation unit 17
The cold heat generated in 1 is taken out to a low temperature tank (not shown) or the like, and is covered with a plate-like body such as stainless steel on the upper portion of the expander body 14.

The crank mechanism section 9 reciprocates by the action of a crank motion using a compression motor and a compression piston 13 as drive sources (not shown). The crank mechanism section 9 of the compression cylinder 12 is reciprocated. A crank chamber 22 having a guide portion 20 formed at the rear and a guide portion 21 below the expansion cylinder 15 is provided. Lubricating oil 23 is stored at the bottom of the crank chamber 22. A crank mechanism 24 is arranged inside. A connecting rod 25 extending from the crank mechanism 24 has a cross guide 26 slidably fitted in a guide receiver 20a of the guide portion 20, and a piston rod 27 communicating with the cross guide 26 is provided in the guide portion 20. The connecting rod 28 extending from the crank mechanism 24 is slidably fitted to the guide receiver 21a of the guide portion 21 while being connected to the rear portion of the compression piston 13 through the through hole 20b. , The piston rod 30 communicating with the cross guide 29 is the expansion piston 1
6 is connected to the rear part.

Reference numeral 31 is a piston seal that disconnects the compression space 11 and the space 32 behind the compression piston 13 from 3
Reference numeral 3 denotes an oil seal that prevents the lubricating oil 23 in the crank chamber 22 from entering the space 32. Further, 34 is a piston seal that disconnects the space 35 behind the freezing generator 17 and the expansion piston 16, and 36 is an oil seal that prevents the lubricating oil 23 in the crank chamber 22 from entering the space 35.

First, when the crank mechanism 24 of the crank mechanism portion 9 is driven by the rotation of a drive motor (not shown), the compression piston 13 in the compression cylinder 12 of the gas compressor 2 moves to the compression space 11 side and the compression space 11 The working gas, such as helium and nitrogen, which is difficult to liquefy, is compressed. The compressed working gas is radiated to the outside by the radiator 6 provided on the outer periphery of the compression cylinder body 10 and cooled to near room temperature, passes through the gas flow path 5, and further the radiator 7 is provided.
It is cooled by and flows into the regenerator 4.

The working gas flowing into the regenerator 4 is cooled by a material having a large specific heat, for example, a regenerator material such as a wire mesh of copper or lead or a ball, and the cooled working gas is frozen by the freezing generator 17 of the expander 3. And the freezing generation unit 17 is in a high pressure state.

Thereafter, the expansion piston 16 in the expansion cylinder 15 of the expander 3 descends with a phase difference of about 90 ° with the compression piston 13. As a result, the high-pressure working gas that has flowed from the regenerator 4 into the freezing generating unit 17 is suddenly expanded by expanding the freezing generating unit 17 as an expansion space, and the pressure of the working gas in the freezing generating unit 17 suddenly drops. Working gas becomes cold.

When the expansion piston 16 starts to rise and the compression piston 13 retracts, the low temperature working gas passes through the regenerator 4 and returns to the compression space 11 through the gas flow path 5. At this time, in the regenerator 4, the regenerator material is cooled and cold heat is stored in the regenerator 4.

One thermal cycle is completed by the above steps, and this step is repeated by the reciprocating movement of the crank mechanism 24 of the crank mechanism section 9. As a result, the temperature of the freezing generator 17 and the temperature of the regenerator 4 gradually drop,
The working gas of the freezing generation part 17 is made into low temperature. In this state, in the freezing take-out unit 8, the cold heat of the freezing generation unit 17 is heat-exchanged with an external low temperature tank or the like as a heat utilization unit (not shown) so that the freezing load of the external low temperature tank or the like becomes the freezing temperature. .

[0016]

However, in the conventional refrigerator described in FIG. 3, the frequency of the drive motor must be changed to keep the refrigerating load at a predetermined temperature, and the refrigerator must be constantly operated. There was a problem of shortening the life of the machine.

That is, conventionally, after the refrigerating load is sufficiently cooled, the frequency of the drive motor is lowered to maintain the refrigerating load at a predetermined temperature, the refrigerating capacity is lowered, and continuous operation is performed to shorten the life of the refrigerator. There was a problem. In addition, a large drive motor is used because a large drive torque is required to drive the vehicle at such a low frequency drive.

In order to solve this, an intermittent control in which the operation of the refrigerator is temporarily stopped after the refrigeration load has been sufficiently cooled and the operation is restarted when the temperature of the refrigeration load rises is conceivable. When the operation of the machine is interrupted, heat leaks from the expansion cylinder 15 and expansion piston 16 having large heat conduction, resulting in a large heat loss and a new problem that the efficiency of the refrigerator decreases.

Therefore, it is an object of the present invention to provide an efficient refrigerating apparatus with a small heat loss even when the refrigerating operation of the refrigerator is interrupted.

[0020]

According to a first aspect of the present invention, a compression space in a compression cylinder and an expansion space in an expansion cylinder are communicated with each other by a flow path passing through a regenerator, and a compression piston of the compression cylinder is provided. The expansion piston of the expansion cylinder is connected to a drive motor via a crank mechanism so as to be reciprocally driven with a predetermined phase difference from each other,
In a refrigerating device that supplies cold heat generated by a heat cycle including an expansion process of a working gas guided from the compression space to the expansion space to a refrigeration load from a refrigeration extraction part,
The refrigeration is connected to the freezing take-out portion and the refrigerating load side, and while the refrigerating operation supplies cold heat to the refrigerating load from the freezing take-out portion via the working fluid, the freezing operation is performed by evaporating the working fluid. A heat pipe is provided to shut off heat between the take-out portion and the refrigeration load.

According to a second aspect of the present invention, the compression space in the compression cylinder and the expansion space in the expansion cylinder are communicated with each other by a flow path via a regenerator, and the compression piston of the compression cylinder and the expansion piston of the expansion cylinder are connected. Are connected to a drive motor through a crank mechanism so that they are reciprocally driven with a predetermined phase difference from each other, and are generated by a thermal cycle including an expansion process of a working gas introduced from the compression space to the expansion space. In a refrigerating device for supplying cold heat from the freezing take-out section to the refrigerating load, the refrigerating take-out section is connected to the refrigerating load side and is joined during refrigerating operation to supply the cold heat from the freezing take-out section to the refrigerating load. Provide a heat conductor that isolates the refrigerating operation from the refrigerating load by separating them when the refrigerating operation is interrupted. It is obtained by the.

[0022]

According to the first aspect of the present invention, cold heat is supplied from the refrigerating and taking-out portion to the refrigerating load through the working fluid by the heat pipe, while when the refrigerating operation is interrupted, the action of the heat pipe is interrupted and the refrigerating and taking-out portion is discharged. The supply to the cold cryostat is interrupted. Thus, when the refrigerating operation is interrupted, heat is cut off between the freezing take-out portion and the low temperature tank, so that loss due to heat leakage can be extremely reduced.

According to the second aspect of the present invention, the heat conductor connecting the refrigerating take-out portion and the refrigerating load supplies cold heat to the refrigerating load from the refrigerating take-out portion, while the heat conductor is separated when the refrigerating operation is interrupted. The supply of cold heat from the freezing take-out section to the low temperature tank is interrupted. With this, when the refrigerating operation is interrupted, heat is cut off between the freezing take-out section and the low temperature tank, so that loss due to heat leakage can be extremely reduced.

[0024]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a partial schematic view of a Stirling refrigerator showing a first embodiment of the present invention. In the figure, the expander 3 expands the compressed gas supplied through the regenerator 4, and the expander 3 has an expansion cylinder 15 vertically arranged inside the expander body 14. The expansion piston 16 is slidable in the vertical direction inside the expansion cylinder 15.
And a freezing generator 17 is formed inside the expander 3 as an expansion space in which a low temperature is generated.

The regenerator 4 is formed in a cylindrical shape between the inner circumference of the expander main body 14 and the outer circumference of the expansion cylinder 15, and the compressed working gas supplied to the expander 3 through the gas flow path 5. On the other hand, when the working gas expanded and cooled in the freezing generation section 17 is returned to the gas compressor 2, the refrigerant is cooled and stores cold. Stainless steel, lead, and the like are used, and they are formed into a cylindrical shape having a large number of fine holes through which a working gas passes.

The gas flow path 5 is a pipe for connecting the gas compressor 2 and the expander 3 so that the compressed working gas uniformly passes through the regenerator 4 at the inlet side of the regenerator 4. The radiator 7 lowers the compressed high-temperature working gas to around room temperature, and the radiator 7 has a large number of circular fins provided upright on the outside of the body of the expander body 14. Frozen take-out section 8
Is for taking out the cold heat generated in the freezing generation unit 17 to the outside described later, and is covered with a plate-shaped body of stainless steel on the upper portion of the expander body 14.

The heat pipe 37 takes out cold heat from the freezing take-out unit 8 during the freezing operation of the Stirling refrigerating machine 1 and supplies it to a low temperature tank 38 which will be described later. The heat pipe 37 is insulated from the heat pipe 37, and a cutout opening is formed in the upper portion of the heat pipe 37.
Is joined to the upper surface of a plate-shaped body of stainless steel or the like to form the upper end joint 37a, and the cutout opening formed in the lower portion of the heat pipe 37 is joined to the refrigeration load joint 39 to form the lower end joint 37a.
As b, the working fluid 40 such as nitrogen is sealed inside.

The low temperature tank 38 stores a refrigerating load 43 such as a sample, and is filled with a heat insulating material 41 having a thickness sufficient to insulate the inside of the box-shaped body to form a storage chamber 42, and an opening portion thereof is formed. The lower end joint 3 of the heat pipe 37 is mounted on the heat pipe 37 by attaching the refrigerating load joint 39 made of copper or the like having good heat conduction to the portion 42 a
It is joined to 7b.

The gas compressor 2, the radiator 7, the crank mechanism 9 and the like, which are not shown, are the same as those in the prior art described in FIG.

First, the compressed working gas generated in the gas compressor 2 (not shown) passes through the gas flow path 5, and then the radiator 7
It is cooled by and flows into the regenerator 4. The working gas that has flowed into the regenerator 4 is cooled by a material having a large specific heat, for example, a regenerator material such as copper or lead wire mesh or spheres, and the cooled working gas flows into the freezing generation section 17 of the expander 3. The freezing generator 17 is in a high pressure state.

Thereafter, the expansion piston 16 in the expansion cylinder 15 descends with a phase difference of about 90 ° with the compression piston 13. Thereby, the freezing generation part 17 as an expansion space is expanded, the high-pressure working gas that has flowed from the regenerator 4 into the freezing generation part 17 is rapidly expanded, and the freezing generation part 17 is expanded.
Since the pressure of the working gas in (2) drops sharply, the working gas becomes low in temperature.

When the expansion piston 16 starts to rise and the compression piston 13 retreats, the low temperature working gas returns to the compression space 11 through the regenerator 4 and the gas flow path 5. At this time, in the regenerator 4, the regenerator material 18 is cooled and cold heat is stored in the regenerator 4.

By the above steps, one heat cycle is completed, and by repeating this step, the temperature of the freezing generation section 17 and the temperature of the regenerator 4 are gradually decreased, and the working gas of the freezing generation section 17 is changed. It is said to be low temperature.

Here, when the refrigerating load 43 of the low temperature tank 38 is not at a predetermined temperature, the operation of the Stirling refrigerator 1 is continued, and the cold heat from the freezing take-out portion 8 is passed through the upper end joint portion 37a of the heat pipe 37. To exchange heat and hydraulic fluid 4
Cool 0.

At this time, the working fluid 40 is cooled and liquefied to absorb the cold heat, and the liquid mass 40 is formed near the upper end joint portion 37a of the heat pipe 37 as shown by the diagonal lines in FIG.
a is formed. Then, due to gravity, the liquid mass 40a of the hydraulic fluid 40 gradually becomes a fluid 40b in the heat pipe 37 and descends, and by the hydraulic fluid 40 at the boundary between the lower end joint portion 37b and the refrigerating load joint portion 39. Retention 40c
Occurs. The staying 40c of the hydraulic fluid 40 is evaporated into a gas 40d at the lower end joint portion 37b, and the latent heat at this time is transferred to the refrigeration load 43 of the storage chamber 42.

The gas 40d of the hydraulic fluid 40 rises as shown by the white arrow in the figure, and once again becomes the liquid mass 40a due to the cold heat of the freezing and taking-out section 8, and then becomes the fluid 40b and descends. As a result, a heat cycle is configured, and the cold heat generated in the freezing generation unit 17 of the Stirling refrigerator 1 is supplied from the freezing take-out unit 8 to the refrigeration load 43 of the low temperature tank 38 via the heat pipe 37.

After that, when the refrigerating load 43 of the low temperature tank 38 reaches a predetermined temperature, the refrigerating operation of the Stirling refrigerator 1 is interrupted.

As a result, the supply of cold heat from the freezing and taking-out portion 8 to the upper end joint portion 37a of the heat pipe 37 is stopped, so that the liquid mass 40a of the upper end joint portion 37a of the heat pipe 37 becomes a gas due to an increase in temperature. ,further,
The fluid 40b in the central portion of the heat pipe 37 becomes a low temperature gas body, and the liquid body of the hydraulic fluid 40 accumulates at the lower end of the heat pipe 37. In this state, the heat pipe is not configured and the working fluid 40 inside does not flow, and the freezing take-out unit 8
The low temperature tank 38 and the low temperature tank 38 are insulated. As a result, even if the freezing operation of the Stirling refrigerator 1 is interrupted, heat leakage from the freezing load 43 via the expansion cylinder 15 and the expansion piston 16 is prevented.

When the refrigerating load 43 of the low temperature tank 38 reaches a predetermined temperature or higher with the passage of time, the Stirling refrigerator 1 starts to operate again and the upper end joint portion 3 of the heat pipe 37.
7a is cooled to form a mass 40a of the liquid material of the hydraulic fluid 40, a heat pipe is configured, and cold heat is supplied to the refrigerating load 43 of the low temperature tank 38. In this way, the heat pipe is configured corresponding to the operating state of the Stirling refrigerator 1, and the cold heat generated in the Stirling refrigerator 1 can be efficiently supplied to the refrigerating load 43 of the low temperature tank 38. Further, since the Stirling refrigerator 1 is not continuously operated, the life of the Stirling refrigerator 1 is extended and the reliability is improved.

Next, a second embodiment of the present invention will be described with reference to FIG.

In the second embodiment, instead of the heat pipe 37 and the low temperature tank 38 of the first embodiment, the heat conducting portion 45 and the low temperature tank 4 are used.
6 and 6 are provided.

The heat conducting section 45 takes out cold heat from the freezing take-out section 8 during the freezing operation of the Stirling refrigerator 1.
While supplying to a low temperature tank 46 described later, when the freezing operation of the Stirling refrigerator 1 is interrupted, the freezing take-out section 8 and the low temperature tank 46 are supplied.
In the heat conducting section 45, the bottom portion of the lower heat conductor 47 is joined to the outside of the center of the refrigerating and taking-out section 8, and the upper portion of the lower heat conductor 47 becomes the lower heat conducting separation section 48. The upper part of the upper heat conductor 49, which is joined together and is capable of expanding and contracting in the vertical direction, is joined to the refrigerating load joining part 58, and the lower part of the upper heat conductor 49 is joined to the upper heat conducting separation part 51. A sliding portion 52 that slides up and down is fixed to the conduction separating portion 51 by a separation surface drive motor 50.

Further, in the heat conducting portion 45, the lower portion of the gas sealing container 54 in which the working fluid 53 is sealed is joined to the freezing take-out portion 8, and the upper portion of the gas sealing container 54 is insulative member 54a.
Is connected to the bottom of a low-temperature tank 46 described later, and the separation surface drive motor 50 is fixed inside the upper part of the gas filling container 54, and when the Stirling refrigerator 1 is in a freezing operation, the upper heat conduction separation part 51 and the lower heat conduction separation part 51 are connected. The separation section 48 is brought into contact with
In addition, the separation surface drive motor 50 operates so that the upper heat conduction separation portion 51 and the lower heat conduction separation portion 48 are separated when the Stirling refrigerator 1 suspends the refrigeration operation.

The low temperature tank 46 stores a refrigerating load 55 such as a sample, and is filled with a heat insulating material 56 having a thickness sufficient to insulate the inside and outside of the box-shaped body, and a storage chamber 57 is formed inside.
The opening 57a of the storage chamber 57 is fitted with a refrigeration load joint 58 made of, for example, copper, which has good heat conduction.

The expander 3 and the regenerator 4 are the same as those described in the first embodiment shown in FIG. 1, and the gas compressor 2, the radiator 6 and the crank mechanism 9 which are not shown are shown in FIG. Is the same as that described in.

With the above configuration, the refrigerating load 55 of the low temperature tank 46
Is not at a predetermined set temperature, the Stirling refrigerator 1 continues to operate and the separation surface drive motor 5
At 0, the upper heat conduction separating portion 51 of the upper heat conductor 49 is in contact with the lower heat conducting separation portion 48. At this time, the working fluid 5 in the gas sealing container 54 is cooled by the cold heat of the freezing / unloading section 8.
3. For example, nitrogen is cooled and becomes liquid,
A liquid surface 59 is formed by adhering to the contact surfaces of the upper heat-conducting separating portion 51 and the lower heat-conducting separating portion 48 to improve the heat conduction of the contact surfaces.

As a result, cold heat is transferred from the freezing and taking-out section 8 by heat conduction to the lower heat conductor 47, the lower heat conduction separation section 48 and the liquid surface 59, and further the upper heat conduction separation section 51 and the upper heat conduction body 49. It is conducted to the refrigerating load joint 58 via. Therefore, in the low temperature tank 46, the cold heat is heat-exchanged by the refrigeration load joint portion 58, and the cold heat is supplied to the refrigeration load 55.

After that, when the refrigerating load 55 of the low temperature tank 46 reaches a predetermined temperature, the refrigerating operation of the Stirling refrigerator 1 is interrupted, and the separation surface drive motor 50 is driven to drive the lower heat conduction separating portion 48 and the upper heat conduction. The separation unit 51 is separated. As a result, the heat conduction between the freezing take-out section 8 and the low temperature tank 46 is completely cut off, so that the heat leak from the freezing load 55 through the expansion cylinder 15, the expansion piston 16 and the like is prevented.

When the refrigerating load 55 of the low temperature tank 46 reaches a predetermined temperature or higher, the Stirling refrigerator 1 starts the refrigerating operation again, and the separation surface driving motor 50 drives the upper heat conducting separation of the heat conducting portion 45. The portion 51 contacts the lower heat conducting separation portion 48. As a result, the cold heat is supplied to the low temperature bath 46 again from the freezing and taking-out section 8.

As described above, since the heat conduction state is coupled and separated according to the operating state of the Stirling refrigerator 1,
The cold heat can be efficiently supplied to the refrigeration load 55 of the low temperature tank 46. Further, since the Stirling refrigerator 1 is not continuously operated, the life of the Stirling refrigerator 1 is extended and the reliability is improved.

[0052]

As described above, the invention of claim 1 is
When the refrigeration operation is interrupted, the action of the heat pipe is interrupted and heat is cut off between the refrigeration take-out portion and the refrigeration load, so that the loss due to heat leakage can be extremely reduced. Further, since the refrigeration system is not operated continuously, the life of the refrigeration system is extended and the reliability is improved.

Further, according to the second aspect of the present invention, when the refrigerating operation is interrupted, the heat conductor is separated and heat is cut off between the refrigerating take-out portion and the refrigerating load, so that loss due to heat leakage can be extremely reduced. Further, since the refrigeration system is not operated continuously, the life of the refrigeration system is extended and the reliability is improved.

[Brief description of drawings]

FIG. 1 is a partial schematic view of a Stirling refrigerator showing a first embodiment of the present invention.

FIG. 2 is a partial schematic view of a Stirling refrigerator showing a second embodiment of the present invention.

FIG. 3 is a schematic diagram of a conventional Stirling refrigerator.

[Explanation of symbols]

 1 Stirling Refrigerator 2 Gas Compressor 3 Expander 4 Regenerator 5 Gas Flow Path 8 Refrigerator Extraction Section 9 Crank Mechanism Section 37 Heat Pipe 38 Low Temperature Tank 39 Refrigeration Load Joint 40 Working Fluid 41 Insulation Material 42 Storage Chamber 43 Refrigeration Load 45 Heat conduction part 46 Low temperature tank 47 Lower heat conductor 48 Lower heat conduction separation part 49 Upper heat conductor 50 Separation surface drive motor 51 Upper heat conduction separation part 52 Sliding part 53 Working fluid 54 Gas sealed container 55 Refrigeration load 57 Storage chamber 58 Refrigeration load joint

Claims (2)

[Claims] 1. A compression space in a compression cylinder and an expansion space in an expansion cylinder are connected by a flow path via a regenerator, and the compression piston of the compression cylinder and the expansion piston of the expansion cylinder are mutually predetermined. Is connected to a drive motor through a crank mechanism so as to be reciprocally driven with a phase difference of 1), and the refrigerating and taking-out section produces cold heat generated by a heat cycle including an expansion process of a working gas guided from the compression space to the expansion space. In the refrigerating device for supplying the refrigerating load from the freezing take-out part and the refrigerating load side, during the refrigerating operation, the cold heat is supplied from the freezing take-out part to the refrigerating load through the working fluid, while the refrigerating operation is interrupted. A heat pipe is provided to shut off heat between the refrigerating unit and the refrigerating load by evaporating the working fluid. Refrigeration apparatus according to claim. 2. A compression space in the compression cylinder and an expansion space in the expansion cylinder are connected by a flow path via a regenerator, and the compression piston of the compression cylinder and the expansion piston of the expansion cylinder are mutually predetermined. Is connected to a drive motor through a crank mechanism so as to be reciprocally driven with a phase difference of 1), and the refrigerating and taking-out section produces cold heat generated by a heat cycle including an expansion process of a working gas guided from the compression space to the expansion space. In the refrigerating device for supplying cold heat to the refrigerating load from the freezing takeout unit and the refrigerating load side, the refrigerating load is joined to supply the cold heat from the freezing takeout unit to the refrigerating load while the refrigerating operation is interrupted. A cooling body is provided, which is provided with a heat conductor that cuts off heat between the refrigeration take-out portion and the refrigeration load by separating them. Apparatus.