JP2005127215A - Transition critical refrigerant cycle device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a transition critical refrigerant cycle device capable of being miniaturized at low cost by simplifying a structure without installing a conventional heat exchanger for intercooling and a circuit for intercooling for connecting the same. <P>SOLUTION: This transition critical refrigerant device is constructed by connecting a compressor 10, a gas cooler 154, a restriction means 156 and an evaporator 157 in turn, and a high pressure side thereof gets super critical pressure. The compressor 10 is provided with a plurality of steps of compression elements 32, 34. Delivered refrigerant of a lower step compression element 32 of those compression elements is delivered in a hermetic vessel 12. A cooling means 13 for radiating heat of the refrigerant is provided in the hermetic vessel 12. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a refrigerant cycle device that is configured by sequentially connecting a compressor, a gas cooler, a throttle means, and an evaporator, and that has a high pressure side at a supercritical pressure.

In this type of conventional refrigerant cycle apparatus, for example, a rotary compressor, a gas cooler, a throttle means (expansion valve, etc.), an evaporator, and the like are sequentially connected in an annular manner to form a refrigerant cycle (refrigerant circuit). Then, the refrigerant gas is drawn into the low pressure chamber side of the cylinder from the suction port of the rotary compression element of the rotary compressor, and is compressed by the operation of the roller and the vane to become high temperature and high pressure refrigerant gas. It is discharged to the gas cooler through the silencer chamber. The refrigerant gas radiates heat in the gas cooler, and is then squeezed by the squeezing means and supplied to the evaporator. Therefore, the refrigerant evaporates, and at that time, the cooling effect is exhibited by absorbing heat from the surroundings. Here, in recent years, in order to deal with global environmental problems, even in this type of refrigerant cycle, carbon dioxide (CO ₂ ), which is a natural refrigerant, is used as a refrigerant without using conventional chlorofluorocarbon, and the high pressure side is used as a supercritical pressure. Devices using transcritical refrigerant cycles to operate have been developed.

In such a transcritical refrigerant cycle device, a receiver tank is provided on the low pressure side between the outlet side of the evaporator and the suction side of the compressor in order to prevent the liquid refrigerant from returning into the compressor and liquid compression. The liquid refrigerant is stored in the receiver tank, and only the gas is sucked into the compressor. And the throttle means was adjusted so that the liquid refrigerant in a receiver tank may not return to a compressor (for example, refer to patent documents 1).
Further, a transcritical refrigerant cycle apparatus as shown in FIG. 5 in which liquid compression in a compressor is eliminated without providing a receiver tank has been proposed.

In FIG. 5, reference numeral 10 denotes an internal intermediate pressure type multi-stage (two-stage) compression rotary compressor, and the lower rotary compression element 32 driven by the electric element 14 in the hermetic container 12 and the rotary shaft 16 of the electric element 14. And an upper rotary compression element 34. The compressor 10 compresses the refrigerant gas sucked from the refrigerant introduction pipe 94 by the lower rotary compression element 32 and discharges the refrigerant gas into the sealed container 12. The intermediate pressure refrigerant gas in the sealed container 12 is temporarily supplied from the refrigerant introduction pipe 92. Discharge to the intermediate cooling circuit 150A.
The intermediate cooling circuit 150A is provided so as to pass through an intermediate cooling heat exchanger (intercooler) 150B, where the refrigerant gas is air-cooled and sucked into the upper rotary compression element 34 and compressed. The refrigerant gas that has become high pressure due to the second-stage compression is discharged from the refrigerant discharge pipe 96 and is air-cooled by the gas cooler 154. The refrigerant that has exited the gas cooler 154 exchanges heat with the refrigerant that has exited the evaporator 157 in the first heat exchanger 160, and then enters the evaporator 157 via the expansion valve 156, evaporates, and passes through the internal heat exchanger 160 again. Then, the refrigerant is sucked from the refrigerant introduction pipe 94 into the lower rotary compression element 32.
The operation in this case will be described with reference to the ph diagram of FIG. The refrigerant is compressed by the lower rotary compression element 32 (obtains enthalpy Δh3) to an intermediate pressure, and the refrigerant discharged into the sealed container 12 (state 2 in FIG. 3) exits from the refrigerant introduction pipe 92 and is an intermediate cooling circuit. Flows into 150A. And it flows in into the heat exchanger 150B for intermediate cooling which this intermediate cooling circuit 150A passes, and is thermally radiated by an air cooling system there (3 state of FIG. 3). Here, the intermediate pressure refrigerant loses enthalpy Δh1 in the intermediate cooling heat exchanger 150B as shown in FIG.
Thereafter, the air is sucked into the upper rotary compression element 34 and compressed in the second stage to become high-pressure and high-temperature refrigerant gas, which is discharged to the outside through the refrigerant discharge pipe 96. At this time, the refrigerant is compressed to an appropriate supercritical pressure (state 4 in FIG. 3).

The refrigerant gas discharged from the refrigerant discharge pipe 96 flows into the gas cooler 154, where it is radiated by the air cooling method (in the state 5 ′ in FIG. 3), and then passes through the first heat exchanger 160. The refrigerant is then further cooled by taking heat away from the low-pressure side refrigerant (state 5 in FIG. 3) (losing enthalpy by Δh2). Thereafter, the refrigerant is depressurized by the expansion valve 156, and in this process, a gas / liquid mixed state is obtained (state 6 in FIG. 3), and then flows into the evaporator 157 and evaporates (state 1 ′ in FIG. 3). ). The refrigerant discharged from the evaporator 157 passes through the first heat exchanger 160, where it is deprived of heat from the high-pressure side refrigerant and heated (state 1 in FIG. 3) (obtains enthalpy Δh2).
The refrigerant heated by the first heat exchanger 160 repeats the cycle of being sucked into the rotary compression element 32 at the lower stage of the rotary compressor 10 from the refrigerant introduction pipe 94.
Japanese Patent Publication No. 7-18602

  However, the transcritical refrigerant cycle apparatus shown in FIG. 5 discharges the intermediate-pressure refrigerant gas discharged into the sealed container 12 from the refrigerant introduction pipe 92 to the intermediate cooling circuit 150A, and the intermediate cooling heat exchanger 150B supplies the refrigerant gas. After the air is cooled, it is sucked into the upper rotary compression element 34 and compressed, so an intermediate cooling heat exchanger (intercooler) 150B and an intermediate cooling circuit 150A for connecting the same are required. As a result, the number of parts increases, resulting in an increase in cost and a problem that the size cannot be reduced.

  The object of the present invention is to solve the conventional problems and to simplify the structure and to reduce the size and size without installing an intermediate cooling heat exchanger or an intermediate cooling circuit for connecting the heat exchanger. It is to provide a transcritical refrigerant cycle device.

The transcritical refrigerant cycle apparatus according to claim 1 of the present invention for solving the above-mentioned problem is a refrigerant cycle apparatus configured by sequentially connecting a compressor, a gas cooler, a throttle means, and an evaporator, wherein the high pressure side has a supercritical pressure. And
The compressor includes a plurality of stages of compression elements in a sealed container, and the refrigerant discharged from the lower stage compression elements of these compression elements is discharged into the sealed container, and cooling means for radiating heat from the refrigerant It is provided in an airtight container.

  The transcritical refrigerant cycle apparatus according to claim 2 of the present invention is the transcritical refrigerant cycle apparatus according to claim 1, wherein the cooling means has an air-cooling surface having a heat dissipating surface fixed to the outer wall surface of the sealed container, or It is a water cooling device.

The transcritical refrigerant cycle apparatus according to claim 1 of the present invention is a refrigerant cycle apparatus configured by sequentially connecting a compressor, a gas cooler, a throttle means, and an evaporator, wherein the high pressure side becomes a supercritical pressure. A plurality of stages of compression elements are provided in the sealed container, and refrigerant (carbon dioxide (CO ₂ ), NO, etc.) discharged from the lower stage of these compression elements is discharged into the sealed container. Because the cooling means for dissipating heat is provided in the sealed container, the cooling means can sufficiently cool, so there is no need to install an intermediate cooling heat exchanger or an intermediate cooling circuit for connecting it. In addition, the temperature rise in the sealed container can be suppressed, the discharge temperature can be reduced, and the input to the electric element can be reduced, so that the compression efficiency in the rotary compression element can be improved and the COP is improved. Rukoto can, moreover structure can turn easily achieves the remarkable effect that allows miniaturization at low cost.

  The transcritical refrigerant cycle device according to claim 2 of the present invention is an air cooling device or a water cooling device in which the cooling means has a heat radiating surface such as a large number of fins fixedly installed on the outer wall surface of the sealed container. The structure is simple, inexpensive, can be downsized, and has a further remarkable effect that the refrigerant discharged from the lower rotary compression element to the inside of the hermetic container can be sufficiently cooled with a high heat dissipation effect.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
(First embodiment)
FIG. 1 is a longitudinal side view of an internal intermediate pressure type multi-stage (two-stage) compression rotary compressor 10 having lower and upper rotary compression elements 32 and 34 as an embodiment of a compressor used in the transcritical refrigerant cycle apparatus of the present invention. FIG. 2 is a refrigerant circuit diagram of the transcritical refrigerant cycle device of the present invention. The transcritical refrigerant cycle device of the present invention is used for vending machines, air conditioners or refrigerators, showcases, and the like.
In each figure, reference numeral 10 denotes an internal intermediate pressure type multistage compression rotary compressor that uses carbon dioxide (CO ₂ ) as a refrigerant. The compressor 10 includes, for example, a cylindrical sealed container 12 made of an aluminum-based metal, and the sealed container 12. The electric element 14 arranged and housed on the upper side of the inner space of the electric element 14 and the lower rotary compression element 32 (first stage) which is arranged below the electric element 14 and is driven by the rotating shaft 16 of the electric element 14 and the upper stage The rotary compression mechanism unit 18 includes a rotary compression element 34 (second stage).
The sealed container 12 has an oil reservoir at the bottom, a container body 12A that houses the electric element 14 and the rotary compression mechanism 18, and a generally bowl-shaped end cap (lid body) 12B that closes the upper opening of the container body 12A. A circular mounting hole 12D is formed in the center of the upper surface of the end cap 12B, and a terminal (wiring is omitted) 20 for supplying power to the electric element 14 is mounted in the mounting hole 12D. It has been.

  Cooling means 13 for cooling the refrigerant discharged from the lower rotary compression element 32 into the sealed container 12 is fixedly installed on the outer wall surface of the container body 12A. The cooling means 13 is composed of, for example, an air cooling device provided with a large number of fins 13A made of an aluminum-based metal.

The electric element 14 is a so-called magnetic pole concentrated winding type DC motor, and includes a stator 22 attached in an annular shape along the inner peripheral surface of the upper space of the hermetic container 12 and a slight gap inside the stator 22. And a rotor 24 inserted and installed. The rotor 24 is fixed to a rotating shaft 16 that passes through the center and extends in the vertical direction.
The stator 22 includes a laminate 26 in which donut-shaped electrode steel plates are laminated, and a stator coil 28 wound around the teeth of the laminate 26 by a direct winding (concentrated winding) method. The rotor 24 is formed of a laminated body 30 of electrode steel plates like the stator 22, and is formed by inserting a permanent magnet MG into the laminated body 30.
An intermediate partition plate 36 is sandwiched between the lower rotary compression element 32 and the upper rotary compression element 34. That is, the lower rotary compression element 32 and the upper rotary compression element 34 include an intermediate partition plate 36, an upper cylinder 38 and a lower cylinder 40 disposed above and below the intermediate partition plate 36, and the upper and lower cylinders 38, 40. The upper and lower rollers 46 and 48 are rotated omnidirectionally by upper and lower omnidirectional portions 42 and 44 provided on the rotating shaft 16 with a phase difference of 180 degrees, and the upper and lower cylinders are in contact with the upper and lower rollers 46 and 48. 38 and 40 are divided into a low pressure chamber side and a high pressure chamber side, respectively, and the upper opening surface of the upper cylinder 38 and the lower opening surface of the lower cylinder 40 are closed to support the bearing of the rotary shaft 16. An upper support member 54 and a lower support member 56 are also used as supporting members.

On the other hand, the upper support member 54 and the lower support member 56 are respectively provided with a suction passage 60 (the upper suction passage is not shown) that communicates with the inside of the upper and lower cylinders 38 and 40 through a suction port (not shown), and a part thereof is recessed. Discharge silencing chambers 62 and 64 formed by closing the recessed portion with an upper cover 66 and a lower cover 68 are provided.
The discharge silencer chamber 64 and the inside of the sealed container 12 are communicated with each other through a communication passage that penetrates the upper and lower cylinders 38 and 40 and the intermediate partition plate 36, and an intermediate discharge pipe 121 is provided upright at the upper end of the communication passage. The intermediate pressure refrigerant gas compressed by the lower rotary compression element 32 is discharged from the intermediate discharge pipe 121 into the sealed container 12.

And, as the refrigerant, the above-mentioned carbon dioxide (CO ₂ ), which is a natural refrigerant in consideration of flammability and toxicity, is used as the refrigerant, and the oil as the lubricating oil is, for example, mineral oil (mineral oil), Existing oils such as alkylbenzene oil, ether oil, ester oil and PAG (polyalkyl glycol) are used.

On the side surface of the container main body 12A of the sealed container 12, the suction passage 60 (upper side is not shown) of the upper support member 54 and the lower support member 56, the discharge silencer chamber 62, the upper side of the upper cover 66 (on the lower end of the electric element 14). The sleeves 142 and 143 are fixed by welding at positions corresponding to the substantially corresponding positions.
In addition, one end of a refrigerant introduction pipe 94 for introducing refrigerant gas into the lower cylinder 40 is inserted and connected in the sleeve 142, and one end of the refrigerant introduction pipe 94 communicates with the suction passage 60 of the lower cylinder 40. The other end of the refrigerant introduction pipe 94 is connected to the first heat exchanger 160. In addition, a refrigerant discharge pipe 96 is inserted and connected into the sleeve 143, and one end of the refrigerant discharge pipe 96 communicates with the discharge silencer chamber 62.

Next, in FIG. 2, the compressor 10 mentioned above comprises a part of refrigerant circuit shown in FIG. That is, the refrigerant discharge pipe 96 of the compressor 10 is connected to the inlet of the gas cooler 154. The piping that exits the gas cooler 154 passes through the first heat exchanger 160. The first heat exchanger 160 is for exchanging heat between the high-pressure refrigerant discharged from the gas cooler 154 and the low-pressure refrigerant discharged from the evaporator 157.
The refrigerant that has passed through the first heat exchanger 160 reaches an expansion valve 156 as a throttle means. The outlet of the expansion valve 156 is connected to the inlet of the evaporator 157, and the piping exiting the evaporator 157 is connected to the refrigerant introduction pipe 94 via the first heat exchanger 160.

Next, the operation of the transcritical refrigerant cycle apparatus of the present invention will be described with reference to the ph diagram (Mollier diagram) of FIG. When the stator coil 28 of the electric element 14 of the compressor 10 is energized via the terminal 20 and a wiring (not shown), the electric element 14 is activated and the rotor 24 rotates. By this rotation, the upper and lower rollers 46 and 48 fitted to the upper and lower eccentric portions 42 and 44 provided integrally with the rotary shaft 16 rotate eccentrically in the upper and lower cylinders 38 and 40.
Accordingly, the refrigerant gas at a low pressure (state 1 in FIG. 3) sucked from the suction port (not shown) to the low pressure chamber side of the cylinder 40 via the suction passage 60 formed in the refrigerant introduction pipe 94 and the lower support member 56. Is compressed by the operation of the roller 48 and the vane 52 to become an intermediate pressure, and is discharged from the intermediate discharge pipe 121 into the sealed container 12 through the communication path (not shown) from the high pressure chamber side of the lower cylinder 40. Thereby, the inside of the sealed container 12 becomes an intermediate pressure (state 2 in FIG. 3).
The refrigerant discharged into the hermetic container 12 is deprived of heat and cooled in the hermetic container 12 cooled by the cooling means 13, and at this time, the enthalpy is lost by Δh1 (state 3 in FIG. 3). The temperature rise in the sealed container 12 can be suppressed, the discharge temperature can be reduced, and the input to the electric element can be reduced. Therefore, the compression efficiency in the upper rotary compression element 34 can be improved, and the COP can be improved.

  The cooled intermediate pressure refrigerant gas is sucked into the low pressure chamber side of the upper cylinder 38 of the upper rotary compression element 34 from a suction port (not shown) via a suction passage (not shown) formed in the upper support member 54. The second stage compression is performed by the operation of the roller 46 and the vane 50 to form a high-pressure and high-temperature refrigerant gas, which passes through a discharge port (not shown) from the high-pressure chamber side and passes through a discharge silencer chamber 62 formed in the upper support member 54. It is discharged to the outside from the discharge pipe 96. At this time, the refrigerant is compressed to an appropriate supercritical pressure (state 4 in FIG. 3).

The refrigerant gas discharged from the refrigerant discharge pipe 96 flows into the gas cooler 154, where it dissipates heat by the air cooling method (5 ′ state in FIG. 3), and then passes through the first heat exchanger 160. The refrigerant is further cooled by taking heat away from the low-pressure side refrigerant (state 5 in FIG. 3).
This state will be described with reference to FIG. That is, when there is no first heat exchanger 160, the enthalpy of the refrigerant at the inlet of the expansion valve 156 is in a state indicated by 5 ′. In this case, the refrigerant temperature in the evaporator 157 increases. On the other hand, when heat exchange is performed with the low-pressure side refrigerant in the first heat exchanger 160, the enthalpy of the refrigerant decreases by Δh2, and is in the state indicated by 5 in FIG. The refrigerant temperature in the evaporator 157 is lowered. Therefore, the cooling capacity of the refrigerant gas in the evaporator 157 improves when the first heat exchanger 160 is provided.
Therefore, it is possible to easily achieve a desired evaporation temperature, for example, an evaporation temperature in the evaporator 157 in the middle high temperature range of + 12 ° C. to −10 ° C. without increasing the refrigerant circulation rate. In addition, power consumption in the compressor 10 can be reduced.

The high-pressure side refrigerant gas cooled by the first heat exchanger 160 reaches the expansion valve 156. At the inlet of the expansion valve 156, the refrigerant gas is still in a gaseous state. The refrigerant is converted into a gas / liquid two-phase mixture (state 6 in FIG. 3) due to the pressure drop in the expansion valve 156, and flows into the evaporator 157 in that state. Therefore, the refrigerant evaporates and exhibits a cooling action by absorbing heat from the air.
Thereafter, the refrigerant flows out of the evaporator 157 (1 ′ state in FIG. 3) and passes through the first heat exchanger 160. Therefore, heat is taken from the refrigerant on the high-pressure side and is subjected to a heating action (state 1 in FIG. 3).
Here, this state will be described with reference to FIG. The evaporator 157 evaporates to a low temperature, and the refrigerant exiting the evaporator 157 is in the state 1 ′ shown in FIG. 3, and the refrigerant is not in a completely gas state but in a liquid mixture. Therefore, by passing through the first heat exchanger 160 and exchanging heat with the high-pressure side refrigerant, the enthalpy of the refrigerant is increased by Δh2, and the state shown in 1 of FIG. 3 is obtained. Thereby, a refrigerant | coolant will be in a gaseous state completely.
The refrigerant in the gaseous state repeats a cycle of being sucked from the refrigerant introduction pipe 94 into the lower rotary compression element 32 of the compressor 10.

(Second Embodiment)
FIG. 4 shows another embodiment of the compressor used in the transcritical refrigerant cycle apparatus of the present invention. In FIG. 4, the same reference numerals as those shown in FIG.
The transcritical refrigerant cycle apparatus of the present invention shown in FIG. 4 is a cooling means 13 instead of an air cooling apparatus having a large number of fins 13A shown in the first embodiment. Except for using a water cooling device in which a metallic cooling pipe 13B having a high thermal conductivity is installed on the outer wall surface of the container body 12A, it is the same as the transcritical refrigerant cycle device of the present invention shown in the first embodiment. The operation of the transcritical refrigerant cycle apparatus of the present invention shown in the second embodiment is described in the same manner as the operation of the transcritical refrigerant cycle apparatus of the present invention shown in the first embodiment using the ph diagram of FIG. Is done.
The transcritical refrigerant cycle apparatus of the present invention shown in FIG. 4 is a cooling means 13 for radiating the refrigerant discharged into the hermetic container 12, and a metallic cooling pipe 13B having high thermal conductivity is provided outside the container main body 12A. Since the water cooling device installed on the wall surface is provided in the sealed container 12, the cooling medium 13 can sufficiently cool the refrigerant discharged into the sealed container 12.

  In the present invention, by using the air cooling device of the first embodiment and the water cooling device of the second embodiment described above, the temperature rise in the sealed container 12 can be suppressed, the discharge temperature can be reduced, and the electric element 14 can be reduced. Therefore, the compression efficiency in the rotary compression elements 32 and 34 can be improved, and the COP can be improved.

  In the above description of the first and second embodiments, an example using an air cooling device or a water cooling device has been shown. However, if the air cooling device and the water cooling device are used, the cooling means can be used. 13 is not limited to these. For example, both an air cooling device and a water cooling device can be used in combination.

  In the examples, carbon dioxide, which is a natural refrigerant that is safe and environmentally friendly from the viewpoint of flammability and toxicity, is used as the refrigerant. However, the invention of claim 1 is not limited thereto, and the transcritical refrigerant cycle is not limited thereto. Various refrigerants that can be used in the above are applicable.

  The description of the above embodiment is for explaining the present invention, and does not limit the invention described in the claims or reduce the scope thereof. Moreover, each part structure of this invention is not restricted to the said embodiment, For example, the following various deformation | transformation are possible within the technical scope as described in a claim.

  In the above description, the two-stage compression type rotary compressor has been described. However, the present invention is not particularly limited in the type of the compressor, and specifically, a reciprocating compressor, a vibration type compressor, a multi-vane type rotary compressor, a scroll type compressor, etc. Further, the number of compression stages may be at least two or more stages.

  In the above description, the example in which the electric element is provided in the sealed container has been described. However, the electric element may be provided outside the sealed container.

  In the above description, the example in which the refrigerant exiting the evaporator passes through the first heat exchanger and exchanges heat with the refrigerant on the high-pressure side is completely gasified. However, the first heat exchanger is Instead of using, a receiver tank may be arranged on the low pressure side between the outlet side of the evaporator and the suction side of the compressor.

  The transcritical refrigerant cycle apparatus of the present invention is a refrigerant cycle apparatus that is configured by sequentially connecting a compressor, a gas cooler, a throttle means, and an evaporator, and has a high-pressure side at a supercritical pressure. The compression refrigerant of the stage is provided, and the discharge refrigerant of the lower compression element among these compression elements is discharged into the sealed container, and the closed container is provided with cooling means for radiating heat of this refrigerant. Therefore, since the cooling means can sufficiently cool, it is not necessary to install an intermediate cooling heat exchanger or an intermediate cooling circuit for connecting it, and the temperature rise in the sealed container can be suppressed and the discharge can be prevented. The temperature can be reduced and the input to the electric element can be reduced, so that the compression efficiency of the rotary compression element can be improved, the COP can be improved, the structure can be simplified, and the cost can be reduced. Since the enabling, high utility value on the industry.

It is explanatory drawing which shows 1 embodiment of the compressor used for the transcritical refrigerant cycle apparatus of this invention. It is a refrigerant circuit diagram of the transcritical refrigerant cycle device of the present invention provided with the compressor shown in FIG. FIG. 6 is a ph diagram of the refrigerant circuit of FIGS. 2 and 5. It is explanatory drawing which shows other embodiment of the compressor used for the transcritical refrigerant cycle apparatus of this invention. It is a refrigerant circuit diagram of the conventional transcritical refrigerant cycle device.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Internal intermediate pressure type multistage (2 stage | paragraph) compression type rotary compressor 12 Airtight container 13 Cooling means 13A Fin 13B Cooling pipe 14 Electric element 32 Lower rotational compression element 34 Upper rotational compression element 94 Refrigerant introduction pipe 96 Refrigerant discharge pipe 154 Gas cooler 156 Expansion valve 157 Evaporator 160 First heat exchanger

Claims (2)

A refrigerant cycle device configured by sequentially connecting a compressor, a gas cooler, a throttle means and an evaporator, wherein the high pressure side is a supercritical pressure,
The compressor includes a plurality of stages of compression elements in a sealed container, and the refrigerant discharged from the lower stage compression elements of these compression elements is discharged into the sealed container, and cooling means for radiating heat from the refrigerant A transcritical refrigerant cycle device provided in an airtight container. 2. The transcritical refrigerant cycle apparatus according to claim 1, wherein the cooling means is an air cooling or water cooling apparatus having a heat radiation surface fixedly installed on an outer wall surface of the sealed container.

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