JP2009287866A - Air cycle refrigerating device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an air cycle refrigerating device capable of preventing decline in freezing capacity due to snow generated along with adiabatic expansion and easily mounted to a container refrigerating unit etc. having a narrow installation space. <P>SOLUTION: In the air cycle refrigerating device, a refrigerant air flow passage 1 in which a plurality of apparatuses for performing heat exchange, compression and expansion of air, respectively and a dehumidification mechanism 9 having a dehumidification function are interposed is provided between an air inlet 1b and an air outlet 1a of a cooled part 10, and air of the cooled part 10 is cooled as a refrigerant. The air cycle refrigerating device is provided with temperature sensors 19, 20 for measuring the temperature within the cooled part 10 and the temperature of the air inlet 1b of the cooled part 10. The air cycle refrigerating device is further provided with a determination means 21 for determining whether or not the dehumidification mechanism 9 is operated based on the measurement result by the temperature sensors 19, 20 and with a dehumidification operation control means 22 for controlling the operation of the dehumidification mechanism 9 based on the determination result of the determination means 21. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an air cycle refrigeration apparatus that uses air as a refrigerant and is used in a refrigeration warehouse, a container refrigeration unit, and the like.

  Since the air cycle refrigeration cooling system uses air as a refrigerant, energy efficiency is insufficient as compared with the case of using chlorofluorocarbon or ammonia gas, but it is preferable in terms of environmental protection. In addition, in facilities where refrigerant air can be directly blown in, such as refrigerated warehouses, the total cost may be reduced by omitting the internal fan, etc., and air cycle refrigeration cooling systems are proposed for such applications. (For example, Patent Document 1).

In the deep cold region of -30 ° C to -60 ° C, it is known that the theoretical efficiency of air cooling is equal to or higher than that of Freon and ammonia gas. However, it is also stated that obtaining the theoretical efficiency of the air cooling is not possible until there is an optimally designed peripheral device. The peripheral device is a compressor, an expansion turbine, or the like.
As the compressor and the expansion turbine, a turbine unit in which a compressor impeller and an expansion turbine impeller are attached to a common main shaft is used (Patent Document 1).

In such an air cycle refrigeration cooling system, when the compressed air is adiabatically expanded, moisture in the air is condensed and snow is generated. Since snow releases heat of condensation when it occurs, the temperature drop during expansion decreases. In addition, snow accumulates in the pipeline from the turbine unit to the cooled part such as a freezer, and the air flow rate may be reduced to lower the refrigeration capacity. In particular, the outlet temperature of the expansion turbine is 20 to 40 ° C. lower than the portion to be cooled, and the moisture in the refrigerant air is solidified and freezing occurs. Therefore, in the conventional air cycle refrigeration cooling system, the snow catcher is provided (patent document 2).
In addition, as a dehumidifying mechanism for dehumidifying the inside of a pipeline, a device using silica gel or a dehumidifier, a device that performs a defrosting operation that sends hot air to the outlet of the turbine unit by changing the piping route, or an expansion turbine An ice collector is installed at the outlet, and a bypass path is provided to change the air path. Hot air is passed from the bypass path to the ice collector to melt the snow and ice collected by the ice collector, and the drain flows out. What is made to perform (patent document 3) etc. is known.
Japanese Patent No. 2623202 JP 2003-279183 A JP 2006-118772 A

  However, the air cycle refrigeration cooling system disclosed in Patent Document 3 requires a bypass path for changing the air path, and there is a problem that the configuration becomes complicated.

  An object of the present invention is to provide an air cycle refrigeration apparatus that can efficiently dehumidify a portion to be cooled with a simple configuration, improve the efficiency of the air expander, and prevent blockage of the flow path due to snow at the outlet of the air expander. That is.

An air cycle refrigeration apparatus according to the present invention includes a refrigerant air flow path including a plurality of devices that respectively perform heat exchange, compression, and expansion of air and a dehumidifying mechanism having a dehumidifying function. In the air cycle refrigeration apparatus that is provided between and cools the air in the cooled part as a refrigerant, a temperature sensor that measures the temperature in the cooled part and the temperature of the air inlet of the cooled part, and a measurement result by the temperature sensor And a dehumidifying operation control unit for controlling the operation of the dehumidifying mechanism based on a determination result of the determining unit.
According to this configuration, the temperature in the cooled part and the temperature of the air inlet of the cooled part are measured by the temperature sensor, and it is determined whether or not to operate the dehumidifying mechanism from the measurement result, and the operation of the dehumidifying mechanism is controlled. . For this reason, there is no need for a complicated configuration such as providing a bypass path in the middle of the refrigerant air flow path, and it is possible to efficiently dehumidify the cooled portion with a simple configuration, and to improve the efficiency of the air expander and at the outlet of the air expander It is possible to prevent blockage of the flow path due to snow.

  In this invention, the said determination means is good also as what determines the dehumidification operation time based on the measurement result of the said temperature sensor. By changing the dehumidifying operation time according to the temperature, appropriate dehumidification can be easily performed.

  In the present invention, as a plurality of devices interposed in the refrigerant air flow path, a compressor having a compressor impeller attached to a main shaft, a turbine impeller attached to the main shaft, and an expansion constituting a turbine unit together with the compressor The heat of the return air from the to-be-cooled part in the heat recovery heat exchanger, comprising a turbine, a heat recovery heat exchanger, pre-compression means, a heat dissipation heat exchanger, and a second heat dissipation heat exchanger Recovery, compression of the heat-recovered air in the pre-compression means, cooling of the compressed air by heat exchange with external air in the heat dissipation heat exchanger, compression of the cooling air by the compressor, this compressed air The second heat radiation heat exchanger is cooled, the cooling air is cooled by the heat recovery heat exchanger, and the cooling air is adiabatically expanded by the expansion turbine. It may be of.

  In the present invention, as a plurality of devices interposed in the refrigerant air flow path, a compressor having a compressor impeller attached to a main shaft, a turbine impeller attached to the main shaft, and an expansion constituting a turbine unit together with the compressor A turbine, a heat exchanger for heat recovery, and a heat exchanger for heat dissipation, wherein the heat recovery heat exchanger recovers heat of the return air from the cooled part, and the pre-compression means of the heat recovered air Compression of the compressed air by heat exchange with the external air in the heat dissipation heat exchanger, compression of the cooling air by the compressor, cooling of the compressed air by the heat recovery heat exchanger, this cooling The adiabatic expansion of the air by the expansion turbine may be sequentially performed.

  In this invention, you may provide the said dehumidification mechanism in the exit part of the said expansion turbine. Thereby, dehumidification can be performed efficiently.

In the present invention, the dehumidifying mechanism may include a heating unit, and the water frozen at the outlet of the expansion turbine may be liquefied by the heating unit and discharged to the outside.
When the cooling proceeds until the inside of the cooled portion is below the freezing point, it is difficult to melt the snow accumulated in the dehumidifying mechanism only by increasing the temperature of the refrigerant air by reducing the rotation speed of the turbine unit. In this case, the rotation of the turbine unit can be slowed, and at the same time, the snow accumulated by the heating means can be melted and reliably liquefied.

  In the present invention, the dehumidifying mechanism may include a cyclone type gas-liquid separation device that performs gas-liquid separation by turning inflowing air along the inner wall surface.

In this invention, the part to be cooled may be a refrigeration container.
In this air cycle refrigeration apparatus, the inside of the cooled part can be dehumidified with a simple configuration, so that it can be easily mounted on a container refrigeration unit having a small installation space.

  An air cycle refrigeration apparatus according to the present invention includes a refrigerant air flow path including a plurality of devices that respectively perform heat exchange, compression, and expansion of air and a dehumidifying mechanism having a dehumidifying function. In the air cycle refrigeration apparatus that is provided between and cools the air in the cooled part as a refrigerant, a temperature sensor that measures the temperature in the cooled part and the temperature of the air inlet of the cooled part, and a measurement result by the temperature sensor And a dehumidifying operation control means for controlling the operation of the dehumidifying mechanism based on the result of the determining means. Therefore, it is possible to improve the efficiency of the air expander and prevent blockage of the flow path due to snow at the outlet of the air expander.

  An embodiment of the present invention will be described with reference to FIGS. FIG. 1 shows the overall configuration of the air cycle refrigeration apparatus of this embodiment. This air cycle refrigeration apparatus is an apparatus that directly cools the air of the cooled portion 10 as a refrigerant, and has a refrigerant air flow path 1 that extends from the air outlet 1a to the air inlet 1b that opens in the cooled portion 10, respectively. Yes. In this refrigerant air flow path 1, a heat recovery heat exchanger 2, a pre-compression means 3, a heat radiation heat exchanger 4, a compressor 6 of an air cycle refrigeration cooling turbine unit 5, a second heat radiation heat exchanger 7, And the expansion turbine 8 of the said turbine unit 5 is provided in order. The heat absorption heat exchanger 2 exchanges heat between the inflow air near the air outlet 1a in the same refrigerant air flow path 1 and the air that has been heated by the subsequent compression and cooled. The air in the vicinity of the air outlet 1a passes through the heat exchanger 2a. Here, a refrigeration container is used as the cooled portion 10.

  The pre-compression means 3 comprises a blower or the like and is driven by a motor 3a. The heat-dissipating heat exchanger 4 and the second heat-dissipating heat exchanger 7 have heat exchangers 4a and 7a for circulating the cooling medium, respectively, and are externally supplied from the cooling tower 11 into the heat exchangers 4a and 7a. Heat exchange is performed between the cooling air that is the refrigerant and the air in the refrigerant air flow path 1.

  The compressor 6 of the turbine unit 5 compresses the return air from the cooled part 10 and the air flowing in through the heat dissipation heat exchanger 4. The second heat radiating heat exchanger 7 exchanges heat between the air compressed by the compressor 6 and high pressure and high temperature, and cooling air that is an external refrigerant supplied from the cooling tower 11. The air compressed by the compressor 6 is primarily cooled. The heat recovery heat exchanger 2 exchanges heat between the air that has been primarily cooled by the second heat radiation heat exchanger 7 and the return air from the cooled portion 10, so that the expansion turbine 8 The compressed air before entering is secondarily cooled. The expansion turbine 8 that constitutes the turbine unit 5 together with the compressor further cools and supplies the compressed air secondarily cooled by the heat recovery heat exchanger 2 to the cooled portion 10 by adiabatic expansion. That is, the air inlet 1 b of the cooled part 10 is the outlet of the expansion turbine 8. The outlet portion is provided with a dehumidifying mechanism 9 having a dehumidifying function. The dehumidifying mechanism 9 is disposed in the cooled part 10.

  This air cycle refrigeration apparatus is an apparatus that keeps the cooled part 10 at about 0 ° C. to −60 ° C., and enters the refrigerant air flow path 1 from the air outlet 1a of the cooled part 10 at about 0 ° C. to −60 ° C. Atmospheric air flows in. Note that the numerical values of temperature and pressure shown below are examples that serve as a rough standard. The air that has flowed into the refrigerant air flow path 1 from the air outlet 1a is used to cool the subsequent air in the refrigerant air flow path 1 by the heat recovery heat exchanger 2 and is heated to 30 ° C. The heated air remains at 1 atm, but is compressed to 1.4 atm by the pre-compression means 3, and the temperature is raised to 70 ° C. by the compression. The heat-dissipating heat exchanger 4 exchanges heat of the heated air at 70 ° C. with cold water or air at a normal temperature and cools it to 40 ° C.

The air at 40 ° C. and 1.4 atm cooled by the heat exchange is compressed to 1.8 atm by the compressor 6 of the turbine unit 5, and is heated to about 70 ° C. by this compression. It is cooled to 40 ° C. by the heat exchanger 7 for use. The 40 ° C. air is cooled to −20 ° C. by the −30 ° C. air in the heat recovery heat exchanger 2. The atmospheric pressure is maintained at 1.8 atmospheric pressure discharged from the compressor 6.
The air cooled to −20 ° C. in the heat recovery heat exchanger 2 is adiabatically expanded by the expansion turbine 8 of the turbine unit 5, cooled to −55 ° C., and discharged from the air inlet 1 b to the cooled portion 10. This air cycle refrigeration cooling apparatus performs such a refrigeration cycle.

  In the turbine unit 5, a compressor impeller 6 a of the compressor 6 and a turbine impeller 8 a of the expansion turbine 8 are respectively attached to both ends of the main shaft 12 that is rotatably supported by the bearing 13. The compressor impeller 6a of the compressor 6 is driven by the power generated in the turbine impeller 6a of the compressor 6.

  The dehumidifying mechanism 9 includes a cyclone type gas-liquid separator shown in FIG. 2 and FIG. 3 in a longitudinal sectional view and a horizontal sectional view, and the cyclone type gas-liquid separator turns the flowing gas along the inner wall surface. It has a cylindrical device body 14 for performing gas-liquid separation. An outlet portion of the expansion turbine 8 (the air inlet 1b of the cooled portion 10) is disposed in the apparatus main body 14, and the cooling air ejected from the outlet turns along the inner wall surface of the apparatus main body 14. One end of the apparatus main body 14 is an open end, and cooling air that has passed through the apparatus main body 14 is supplied to the cooled portion 10 from the open end. FIG. 3 is a cross-sectional view taken along the line III-III in FIG.

The outlet portion 1b of the expansion turbine 8 is composed of an air blowing pipe, and is provided through a part of the peripheral wall in the vicinity of the closed end of the apparatus main body 14 as shown in FIG. 2, and the axis L of the air blowing pipe is shown in FIG. Thus, it arrange | positions so that it may become a position eccentric from the axial center O of the apparatus main body 14. Thereby, the cooling air ejected from the outlet portion 1 b of the expansion turbine 8 can be reliably swirled along the inner wall surface of the apparatus main body 14. At this time, the cooling air becomes a swirling flow, and only moisture contained in the cooling air is pressed against the inner wall surface of the apparatus main body 14 by centrifugal force and separated.
Further, a 10-20 mesh wire net 15 subjected to hydrophilic treatment is stretched on the inner wall surface of the apparatus main body 14. Thereby, it becomes easier to capture the separated moisture on the inner wall surface of the apparatus main body 14.

  Further, as shown in FIG. 4 showing a sectional view taken along the line IV-IV of FIG. 2, the apparatus main body 14 is installed at an inclination angle θ of 5 to 90 degrees with respect to the horizontal plane H with the open end side facing downward. ing. Thereby, the water separated from the cooling air can be flowed to the open end side along the inner wall surface of the apparatus main body 14.

  Further, a water collecting flange 16 that is folded inward is provided on the peripheral edge of the open end of the apparatus main body 14, that is, the peripheral edge of the lower end of the apparatus main body 14 in the inclined posture in FIG. A drain port 17 a that communicates with the drain pipe 17 is provided at the lower position. As a result, the water flowing toward the open end side along the inner wall surface of the apparatus main body 14 is accumulated in the catching flange 16 and discharged from the drain port 17a to the outside of the cooled part 10 through the drain pipe 17. it can.

  The apparatus main body 14 is made of an aluminum alloy, and a heater 18 is provided on the outer periphery thereof. Thereby, when the moisture in the cooling air becomes snow and accumulates on the inner wall surface of the apparatus main body 14, the accumulated snow can be melted and drained by energizing the heater 18.

  In FIG. 1, a temperature sensor 19 for measuring the temperature in the cooled portion 10 and a temperature sensor 20 for measuring the temperature of the air inlet 1b are provided in the cooled portion 10 and its air inlet 1b. Also, a determination unit 21 that determines whether or not to operate the dehumidifying mechanism 9 from the measurement results of the temperature sensors 19 and 20, and the operation of the dehumidifying mechanism 9 according to a setting rule based on the determination result of the determination unit 21 A dehumidifying operation control means 22 for controlling is provided. Here, the determination means 21 determines whether or not to operate the dehumidifying mechanism 9 from the measurement results of the temperature sensors 19 and 20 as the setting rule, and when it is determined to operate, the dehumidifying operation time is also determined. To be determined. That is, dehumidification is efficiently performed by determining the operation interval of the dehumidifying mechanism 9 according to the temperature conditions of the cooled portion 10 and the outlet portion of the expansion turbine 8. Table 1 shows an example of the relationship between the temperature in the cooled portion 10 and the temperature of the outlet portion 1b of the expansion turbine 8 and the dehumidifying operation time determined by the determination means 21.

Next, the operation of the dehumidifying mechanism 9 in this air cycle refrigeration apparatus will be described.
In the initial cooling from the room temperature of the cooled portion 10 made of a refrigerated container, the temperature of the outlet portion of the expansion turbine 8 is equal to or higher than the freezing point of water, so the moisture in the cooling air ejected from the outlet portion is It is liquefied. At this time, due to the swirl flow generated in the device main body 14 of the dehumidifying mechanism 9, the moisture in the cooling air is pressed against the inner wall surface of the device main body 14 and separated from the air. It is drained to the outside of the cooled part 10 through the pipe 17.
When the temperature of the outlet portion of the expansion turbine 8 becomes the freezing point or lower, the moisture in the cooling air becomes snow and accumulates on the inner wall surface of the device main body 14 of the dehumidifying mechanism 9. If the operation is continued as it is, the flow path is closed, so that the rotation of the turbine unit 5 is slowed at a certain time to make the temperature at the outlet of the expansion turbine 8 higher than the freezing point, and the accumulated snow is melted and liquefied. Further, depending on the temperature of the outlet portion of the expansion turbine 8, the heater 18 which is a heating means of the dehumidifying mechanism 9 is energized to melt and liquefy the accumulated snow, and then the turbine unit 5 is accelerated to the rated speed again. The liquefied water is drained with an air stream.
When the cooling further progresses and the inside of the cooled portion 10 becomes below the freezing point (see (4) in Table 1), the turbine unit 5 is rotated at a low speed and the heater 18 of the dehumidifying mechanism 9 is energized at the same time. The snow accumulated on the inner wall surface of 14 is melted and liquefied and drained.

However, if the rotation of the turbine unit 5 is made low for the dehumidifying operation, the refrigerating capacity is lowered, the temperature in the cooled part 10 is increased, and the operation efficiency is deteriorated. Therefore, as shown in Table 1, the dehumidifying operation control means 22 performs operation control so that water is efficiently drained by shortening the low-speed rotation time and the energization time of the heater 18.
Specifically, since the temperature of the outlet portion of the expansion turbine 8 is 10 to 30 ° C. lower than the temperature in the cooled part 10, the temperature in the cooled part 10 is equal to or higher than the freezing point ((1) to (3) in Table 1). However, at the outlet of the expansion turbine 8, moisture in the air becomes snow and accumulates on the inner surface of the apparatus main body 14 in the dehumidifying mechanism 9. In this state, by rotating the turbine unit 5 at a low speed or energizing the heater 18 for a short time, the accumulated snow can be immediately liquefied and efficiently drained with an air flow. Dehumidification can be efficiently performed by shortening the dehumidifying operation interval in this temperature band and increasing the number of operations.
By repeating the above operation, moisture in the cooled portion 10 is dehumidified in the initial stage of cooling, preventing the efficiency of the expansion turbine 8 from decreasing, and preventing the flow path from being blocked due to snow accumulation at the outlet of the expansion turbine 8. To do.

  Thus, according to this air cycle refrigeration apparatus, the temperature in the cooled part 10 and the temperature of the air inlet 1b of the cooled part 10 are measured by the temperature sensors 19 and 20, and the dehumidifying mechanism 9 is operated from the measurement results. Is determined by the determination means 21 and the operation of the dehumidification mechanism 9 is controlled by the dehumidification operation control means 22, so that a complicated configuration such as providing a bypass path in the middle of the refrigerant air flow path 1 is not required, and simple With the configuration, the inside of the cooled portion 10 can be dehumidified, and the efficiency of the expansion turbine 8 can be improved and the flow path blockage due to snow accumulation at the outlet of the expansion turbine 8 can be prevented. This facilitates the mounting of the air cycle refrigeration apparatus to a container refrigeration unit or the like having a small installation space.

  FIG. 5 shows an overall configuration of an air cycle refrigeration apparatus according to another embodiment. In the figure, the determination means 21 and the dehumidifying operation control means 22 in FIG. 1 are not shown, and the devices having the same functions as those in FIG. This air cycle refrigeration apparatus is also an apparatus that directly cools the air of the cooled portion 10 as a refrigerant, and has a refrigerant air flow path 1 that extends from the air outlet 1a that opens to the cooled portion 10 to the air inlet 1b. . A heat recovery heat exchanger 2, a compressor 6 of an air cycle refrigeration turbine unit 5, a heat dissipation heat exchanger 7, and an expansion turbine 8 of a turbine unit 65 are sequentially provided in the refrigerant air flow path 1. The dehumidifying mechanism 9 is provided at the air inlet 1b of the cooled part 10 serving as the outlet part of the expansion turbine 8, the temperature sensors 19 and 20 are provided in the cooled part 10 and the outlet part of the expansion turbine 8, etc. Is the same as in FIG.

This air cycle refrigeration apparatus is also an apparatus that keeps the cooled part 10 at about 0 ° C. to −60 ° C., and enters the refrigerant air flow path 1 from the air outlet 1a of the cooled part 10 at about 0 ° C. to −60 ° C. Atmospheric air flows in. The air that has flowed into the refrigerant air flow path 1 from the air outlet 1a is used to cool the subsequent air in the refrigerant air flow path 1 by the heat recovery heat exchanger 2 and is heated to 30 ° C. The heated air flows into the compressor 6 of the turbine unit 5 while maintaining 1 atm, where it is compressed to a pressure of 1.8 atm, and the temperature is raised to 110 ° C. by the compression. The compressed air is primarily cooled to 40 ° C. by the heat dissipation heat exchanger 7.
The compressed air at 40 ° C. that has been primarily cooled by the heat dissipation heat exchanger 7 is further cooled to −20 ° C. by the heat recovery heat exchanger 2. The pressure is maintained at 1.8 atm discharged from the compressor 6.
The air cooled to −20 ° C. by the heat recovery heat exchanger 2 is adiabatically expanded by the expansion turbine 8 of the turbine unit 5, cooled to −50 ° C., discharged from the air inlet 1 b, and passed through the dehumidifying mechanism 9. It is supplied into the cooling unit 10. This cooling cycle refrigeration apparatus performs such a refrigeration cycle. The dehumidifying operation performed by the dehumidifying mechanism 9, the temperature sensors 19 and 20, the determining unit 21, the dehumidifying operation control unit 22, and the like are the same as in the previous embodiment.

1 is a system diagram of an air cycle refrigeration apparatus according to an embodiment of the present invention. It is a longitudinal cross-sectional view of the cyclone type gas-liquid separator in the same air cycle refrigeration apparatus. It is the III-III arrow sectional drawing in FIG. It is IV-IV arrow sectional drawing in FIG. It is a systematic diagram of the air cycle refrigeration apparatus concerning other embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Refrigerant air flow path 1a ... Air outlet 1b ... Air inlet (exit part of an expansion turbine)
2 ... Heat recovery heat exchanger 3 ... Preloading means 4 ... Heat dissipation heat exchanger 5 ... Turbine unit 6 ... Compressor 6a ... Compressor impeller 7 ... Second heat dissipation heat exchanger 8 ... Expansion turbine 8a ... Turbine impeller DESCRIPTION OF SYMBOLS 9 ... Dehumidification mechanism 10 ... Cooled part 12 ... Main shaft 18 ... Heater (heating means)
19, 20 ... temperature sensor 21 ... determination means 22 ... dehumidification operation control means

Claims (8)

A refrigerant air flow path, in which a plurality of devices each performing heat exchange, compression, and expansion of air and a dehumidifying mechanism having a dehumidifying function are interposed, is provided between the air inlet and the air outlet of the cooled part, and the cooled part In the air cycle refrigeration system that cools the air as a refrigerant,
A temperature sensor for measuring the temperature in the cooled portion and the temperature of the air inlet of the cooled portion; a determining means for determining whether or not to operate the dehumidifying mechanism from a measurement result by the temperature sensor; and a determination of the determining means An air cycle refrigeration apparatus comprising a dehumidifying operation control means for controlling the operation of the dehumidifying mechanism based on the result.   2. The air cycle refrigeration apparatus according to claim 1, wherein the determination unit determines a dehumidifying operation time based on a measurement result of the temperature sensor. 3. The compressor according to claim 1, wherein the plurality of devices interposed in the refrigerant air flow path include a compressor having a compressor impeller attached to a main shaft, a turbine impeller attached to the main shaft, and a turbine together with the compressor. An expansion turbine constituting the unit, a heat recovery heat exchanger, a pre-compression means, a heat dissipation heat exchanger, and a second heat dissipation heat exchanger;
Heat recovery of return air from the cooled part in the heat recovery heat exchanger, compression of the heat recovered air in the pre-compression means, external air of the compressed air in the heat dissipation heat exchanger Cooling by heat exchange with the compressor, compression of the cooling air by the compressor, cooling of the compressed air by the second heat dissipation heat exchanger, cooling of the cooling air by the heat recovery heat exchanger, An air cycle refrigeration apparatus that sequentially performs adiabatic expansion by the expansion turbine. 3. The compressor according to claim 1, wherein the plurality of devices interposed in the refrigerant air flow path include a compressor having a compressor impeller attached to a main shaft, a turbine impeller attached to the main shaft, and a turbine together with the compressor. The unit includes an expansion turbine, a heat recovery heat exchanger, and a heat dissipation heat exchanger.
Heat recovery of return air from the cooled part in the heat recovery heat exchanger, compression of the heat recovered air in the pre-compression means, external air of the compressed air in the heat dissipation heat exchanger Cycle refrigeration in which cooling by heat exchange with the compressor, compression of the cooling air by the compressor, cooling of the compressed air by the heat exchanger for heat recovery, and adiabatic expansion of the cooling air by the expansion turbine are sequentially performed. apparatus.   5. The air cycle refrigeration apparatus according to claim 3, wherein the dehumidifying mechanism is provided at an outlet portion of the expansion turbine.   6. The air cycle refrigeration apparatus according to claim 5, wherein the dehumidifying mechanism includes a heating unit, and moisture frozen at an outlet portion of the expansion turbine is liquefied by the heating unit and discharged to the outside.   The air cycle refrigeration apparatus according to any one of claims 1 to 6, wherein the dehumidifying mechanism includes a cyclone type gas-liquid separator that performs gas-liquid separation by swirling the inflowing air along the inner wall surface.   The air cycle refrigeration apparatus according to any one of claims 1 to 7, wherein the portion to be cooled is a refrigeration container.

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