JP2009014291A - Air cycle refrigerating device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an air cycle refrigerating device capable of manufacturing a heat exchanger as a component at a low cost, and capable of reducing the pressure loss of an air passage in the heat exchanger. <P>SOLUTION: With respect to inflow air, compression by an air compressor of a turbine unit, cooling by a radiating heat exchanger, and adiabatic expansion by an air expander of the turbine unit are sequentially carried out, and the air is supplied into a cooled part, and return air from the cooled part is circulated into the air compressor as the inflow air. A heat recovery heat exchanger is arranged between the air passage between the heat radiating heat exchanger and the air expander and the air passage between the cooled part and the air compressor so as to perform air-air heat exchange of the air flowing in both the air passages, and the air before entering the air expander is cooled by the return air from the cooled part. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an air cycle refrigeration apparatus in which air is used as a refrigerant, and is used in a freezer warehouse, a low temperature room below zero degrees, air conditioning, and the like.

As this type of air cycle refrigeration apparatus, one having a configuration in which air serving as a refrigerant is circulated between a turbine unit having an air compressor and an air expander and a portion to be cooled is known (for example, Patent Document 1). 2). In this air cycle refrigeration system, the return air from the part to be cooled flows into the air compressor of the turbine through the heat recovery heat exchanger. The air compressed by the air compressor passes through the heat dissipating heat exchanger and the heat recovery heat exchanger, flows into the air expander of the turbine, and the air adiabatically expanded by this air expander is supplied to the cooled part. The In the heat-dissipating heat exchanger, the air that has been compressed by the air compressor and becomes high temperature and pressure is primarily cooled by heat exchange with the external medium (heat is transferred from the air passing through the air compressor to the external medium). . In the heat recovery heat exchanger, the air that has been primarily cooled through the heat dissipation heat exchanger exchanges heat with the low-temperature return air from the cooled part (from the air that has passed through the heat dissipation heat exchanger to the return air). The secondary air is cooled by the transfer of heat, and the return air is heated. When an air-to-air heat exchanger is used as the heat recovery heat exchanger or heat dissipation heat exchanger, a plate heat exchanger or a fin tube heat exchanger is used. In addition, there is an example in which a heat exchanger using a liquid as a medium is used (for example, Patent Document 3).
JP 2007-057109 A JP 2007-057143 A JP 2006-118773 A

However, when a plate heat exchanger is used as the heat exchanger of the air cycle refrigeration system having the above configuration, air drift in the heat exchanger is unavoidable, and the designed performance cannot be obtained. There is. In addition, the plate heat exchanger has a problem of high price. On the other hand, although the finned tube heat exchanger is inexpensive, there is a problem that the ventilation resistance on the tube side is high and the pressure loss is large.
Further, in the case of using a liquid as a medium, there is a problem that the cost increases because a pump for circulating the liquid is added. When used in a heat recovery heat exchanger, the liquid flow rate needs to be adjusted in accordance with the air flow rate when air-to-liquid and liquid-to-air heat exchange is performed.

  An object of the present invention is to provide an air cycle refrigeration apparatus capable of manufacturing a heat exchanger as a component at low cost and reducing pressure loss in an air path in the heat exchanger.

The air cycle refrigeration apparatus according to the present invention compresses a turbine unit having an air compressor and an air expander by the air compressor, cools by a heat exchanger for heat dissipation, and the air expander of the turbine unit with respect to inflow air. The air that has been subjected to adiabatic expansion in order is supplied to the part to be cooled, the return air from the part to be cooled is circulated to the air compressor as the inflow air, and the air between the heat exchanger for heat radiation and the air expander A heat recovery heat exchanger that performs heat-to-air heat exchange between the air path and the air path between the part to be cooled and the air compressor, before entering the air expander Is an air cycle refrigeration apparatus that cools the air with the return air from the part to be cooled, and the heat of one of the heat exchanger for heat dissipation and the heat exchanger for heat recovery or the heat of both Exchanger The present invention uses a finned tube heat exchanger in which a plurality of parallel tubes through which high-temperature air flows and a plurality of heat exchange units having fins provided between the tubes are installed in parallel. .
Fin tube heat exchangers are used for automobiles, such as radiators, condensers, and intercoolers, and existing products can be obtained at low cost. Therefore, if a finned tube heat exchanger is used as the heat exchanger for heat dissipation and the heat exchanger for heat recovery, these heat exchangers can be configured at low cost.
Further, in the finned tube heat exchanger, the pressure loss in the air passage on the tube side becomes a problem. However, as described above, a plurality of tubes arranged in parallel and heat having fins provided between these tubes are used. Since a plurality of exchange units are installed in parallel to form a finned tube heat exchanger, and the total amount of air is distributed and passed through the tubes arranged in parallel, pressure loss in the tubes can be reduced.
The air flowing from the air compressor to the air expander of the turbine unit becomes high-temperature and high-pressure air. However, in the heat-dissipating heat exchanger, the tube carries the air passage through which the high-temperature air flows, and is used for heat recovery. In the heat exchanger, since the tube serves as an air passage through which high-temperature air flows, high-pressure air is allowed to flow through a tube having sufficient pressure resistance, and piping becomes easy. Moreover, since the high-pressure air has a smaller volume flow rate than the low-pressure air, this point is also advantageous for pressure loss. As a result, the heat exchanger which is a component can be manufactured at low cost, and the pressure loss of the air path in the heat exchanger can be reduced.

In the present invention, a plurality of rectifying partitions may be provided in the gap between the fins of adjacent heat exchange units arranged side by side. In this case, there are two tubes of the heat exchange unit, and the fins are provided between the two tubes, respectively, and a plurality of parallel heat conductive plates arranged in the longitudinal direction of the tubes, You may consist of a fin element arrange | positioned between heat conductive board | plate materials.
By providing a partition in the gap between the fins in this way, mixing of the air passing through the fin side is suppressed, the fin side air temperature near the outlet of the tube side path can be kept low, and the temperature efficiency of the heat exchanger is improved. can do. When the fin is composed of a plurality of parallel heat conductive plates and fin elements as described above, the provision of the partition has a great effect of suppressing temperature mixing and improving temperature efficiency.

  In this invention, the turbine unit attaches the compressor impeller of the air compressor and the turbine impeller of the air expander to a common main shaft, and drives the compressor impeller by power generated by the turbine impeller. The main shaft may be rotatably supported by a bearing, and a part or all of the thrust force applied to the main shaft may be supported by an electromagnet. In this configuration, since some or all of the thrust force applied to the main shaft is supported by an electromagnet, the thrust force acting on the main shaft rotation support bearing is reduced while suppressing increase in torque in a non-contact manner. Long-term durability and life can be improved. Due to the support by the electromagnet, unlike the permanent magnet, it is also possible to control the appropriate electromagnetic attractive force according to the thrust force acting on the main shaft. Since the long-term durability of the main shaft bearing is improved, the reliability of the entire air cycle refrigeration apparatus is improved.

In this invention, the turbine unit has a motor rotor attached to a common main shaft to which a compressor impeller of the air compressor and a turbine impeller of the air expander are attached, and the main shaft is rotated by the motor. May be.
When the motor is provided to drive the main shaft, the air compressor can be driven without adding auxiliary means for the air compressor, and the apparatus can be made compact.

  The air cycle refrigeration apparatus according to the present invention compresses a turbine unit having an air compressor and an air expander by the air compressor, cools by a heat exchanger for heat dissipation, and the air expander of the turbine unit with respect to inflow air. The air that has been subjected to adiabatic expansion in order is supplied to the part to be cooled, the return air from the part to be cooled is circulated to the air compressor as the inflow air, and the air between the heat exchanger for heat radiation and the air expander A heat recovery heat exchanger that performs heat-to-air heat exchange between the air path and the air path between the part to be cooled and the air compressor, before entering the air expander The air cycle refrigeration system cools the air with the return air from the cooled part, and a plurality of parallel tubes that flow high-temperature air to the heat dissipation heat exchanger and the heat recovery heat exchanger , And Since a finned tube heat exchanger in which a plurality of heat exchange units having fins provided between these tubes are installed in parallel is used, the heat exchanger as a component can be manufactured at low cost, and the air in the heat exchanger The pressure loss of the path can be reduced.

  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 a cooled portion 10 such as a refrigeration warehouse as a refrigerant, and an air circulation path from an air intake port 1a that opens to the cooled portion 10 to an exhaust port 1b. 1 In this air circulation path 1, an air compressor 6 of an air cycle refrigeration turbine unit 5, a heat exchanger 2 for heat dissipation, a heat exchanger 3 for heat recovery, and an air expander 7 of the turbine unit 5 are provided in this order. Yes.

  The air compressor 6 of the turbine unit 5 compresses the return air from the cooled portion 10 and flowing in through the heat recovery heat exchanger 3. The heat dissipating heat exchanger 2 includes an air path 1d through which air compressed to the high pressure and high temperature is compressed by the air compressor 6 and an air path 8 of cooling air that is an external refrigerant supplied from a cooling tower or the like. In the meantime, heat exchange between air and air flowing through the air paths 1d and 8 is performed to primarily cool the air compressed by the air compressor 6. The heat recovery heat exchanger 3 includes both an air path 1e between the heat dissipation heat exchanger 2 and the air expander 7, and an air path 1c between the cooled portion 10 and the air compressor 6. Heat exchange between air and air flowing through the air paths 1e and 1c is performed, and the compressed air before entering the air expander 7 is secondarily cooled. The air expander 7 of the turbine unit 5 further cools and supplies the compressed air secondarily cooled by the heat recovery heat exchanger 3 to the cooled portion 10 by adiabatic expansion.

  This air cycle refrigeration apparatus is an apparatus that keeps the cooled part 10 at about 0 ° C. to −60 ° C., and is 0 ° C. to −60 ° C. at a pressure of 0.1 Mpa from the cooled part 10 to the inlet 1a of the air circulation path 1. About 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 intake port 1a is used for cooling the downstream air in the air circulation path 1 by heat exchange in the heat recovery heat exchanger 3, and the temperature is raised to 30 ° C. The heated air flows into the air compressor 6 of the turbine unit 5 with the pressure of 0.1 Mpa, where it is compressed to a pressure of 0.18 Mpa, 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 2.

The 40 ° C. compressed air that has been primarily cooled by the heat dissipating heat exchanger 2 is further cooled to −20 ° C. by the heat recovery heat exchanger 3. The pressure is maintained at 0.18 MPa discharged from the air compressor 6.
The air cooled to −20 ° C. by the heat recovery heat exchanger 3 is adiabatically expanded by the air expander 7 of the turbine unit 5, cooled to −50 ° C., and supplied from the outlet 1 b to the cooled part 10. . This cooling cycle refrigeration apparatus performs such a refrigeration cycle.

  2-5 shows the specific example of the heat exchanger 2 for thermal radiation, and the heat exchanger 3 for heat recovery. These heat exchangers 2 and 3 are fin tube heat exchangers. As shown in the perspective view of FIG. 5, the finned tube heat exchanger in this case includes a pair of parallel tubes 11A and 11B through which high-temperature air flows and fins provided between the pair of tubes 11A and 11B. A plurality of heat exchange units 9 having 12 are installed in parallel. In FIG. 5, the fins 12 are schematically shown.

  Specifically, the fin 12 is configured as shown in FIG. The figure shows a front view of the heat exchange unit 9. As shown in the figure, the fin 12 includes a plurality of parallel heat conductive plates 24 straddling a pair of parallel tubes 11A, 11B arranged in the longitudinal direction of the tubes 11A, 11B, and between the adjacent heat conductive plates 24, 24. The fin element 12a is arranged and configured. The fin element 12a is formed, for example, by bending a thin metal plate into a corrugated plate shape that is a V-shaped wave. 2 and 4, the arrow on the heat conductive plate 24 indicates the direction of heat conduction in the heat conductive plate 24.

  FIG. 2 shows a side cross-sectional view of the finned tube heat exchanger. As shown in the figure, one end side of the pair of tubes 11A and 11B in each heat exchange unit 9 is communicated with a communication space 25 partitioned from the outside by a partition wall 26, whereby each pair of heat exchange units 9 is connected. The tubes 11 </ b> A and 11 </ b> B and the communication space 25 constitute a U-shaped air path.

  In each heat exchange unit 9, the opening end on the opposite side to the opening end opened in the communication space 25 of one tube 11A is gathered in a common vent hole 27A. Moreover, the opening end on the opposite side to the opening end opened to the communication space 25 of the other tube 11B in each heat exchange unit 9 is also gathered in another common vent hole 27B. Here, one vent 27A is used as an inlet for high-temperature air, and the other vent 27B is used as an outlet for high-temperature air.

  As shown in FIGS. 2 and 3, the heat exchange units 9 are housed in a common case 28 to form a path for low-temperature air, with an inlet 28A at one end of the path and an outlet 28B at the other end. It is configured.

  When the fin-tube heat exchanger having the above-described configuration is used as the heat-dissipating heat exchanger 2, the high-temperature air passage formed by the tubes 11A and 11B and the communication space 25 becomes the air passage 1d in FIG. The low-temperature air passage becomes the cooling air passage 8 in FIG. Further, when used as the heat recovery heat exchanger 3, the high-temperature air passage formed by the tubes 11A and 11B and the communication space 25 becomes the air passage 1c in FIG. 1, and the low-temperature air passage in which the fins 12 are arranged is illustrated. 1 is the air passage 1e for the compressed air in the air.

  Fin tube heat exchangers are used for automobiles, such as radiators, condensers, and intercoolers, and existing products can be obtained at low cost. Therefore, as described above, when a finned tube heat exchanger is used as the heat dissipation heat exchanger 2 and the heat recovery heat exchanger 3 of the air cycle refrigeration apparatus, the heat exchangers 2 and 3 can be configured at low cost. .

  In the finned tube heat exchanger, pressure loss in the air passage on the tube side becomes a problem. However, in this air cycle refrigeration apparatus, a plurality of heat exchange units 9 having a pair of tubes 11A and 11B arranged in parallel and fins 12 provided between the pair of tubes 11A and 11B are installed in parallel. Since the finned tube heat exchanger is configured and the total air amount is dispersed and passed through the tubes 11A and 11B arranged in parallel, the pressure loss in the tubes 11A and 11B can be reduced.

In this air cycle refrigeration apparatus, the air flowing through the air passage from the air compressor 6 to the air expander 7 of the turbine unit 5 in FIG. 1 becomes high-pressure air. In the heat exchanger 2 for heat radiation, this air passage is an air passage 1d through which high-temperature air flows, and the tubes 11A and 11B serve as this air passage, so that the air passage has sufficient strength against high-pressure air. Become. In the heat recovery heat exchanger 3, the air passage through which high-pressure air flows is the air passage 1e through which high-temperature air flows. Similarly, the tubes 11A and 11B serve as this air passage. It will have sufficient strength. Moreover, since the high-pressure air has a smaller volume flow rate than the low-pressure air, this point is also advantageous for pressure loss.
On the other hand, in the fin-tube heat exchanger having the above-described configuration, the air passage in which the fins 12 serving as low-temperature air passages are used as the heat-dissipating heat exchanger 2, when cooling air is supplied from a cooling tower or the like as shown in FIG. It is the air passage 8 on the heat radiation side to be supplied, and when used as the heat recovery heat exchanger 3, it is the air passage 1c through which return air from the cooled portion 10 flows. The pressure of the air flowing through both the air passages 1c and 8 is about 0.1 Mpa, and as shown in FIGS. 2 and 3, the entire finned tube heat exchanger is covered with a simple case 28 so that the temperature can be easily lowered. An air passage can be formed.

  By the way, in the fin tube type heat exchanger having the above-described configuration used as the heat dissipation heat exchanger 2 and the heat recovery heat exchanger 3, as shown in a plan view in FIG. A gap G is generated between 12. In addition, the arrow on the fin 12 in the figure shows the heat conduction direction. In this heat exchanger, the flow of high-temperature air (tubes 11A, 11B side) and the flow of low-temperature air (fin 12 side) are cross-flow heat exchangers that are orthogonal to each other. Thus, large temperature distribution arises in each fin 12 and tube 11A, 11B. For this reason, even low temperature air having a uniform input temperature has a temperature distribution when it passes through the first stage fin 12. Here, since there is a gap G between the fins 12 and 12 described above, the outlet air of the fins 12 is mixed with the nearby air. If such a phenomenon is repeated a plurality of times each time it passes through each fin 12, a temperature distribution as shown in FIG. 7 is generated in the low-temperature air, and the high-temperature air that has passed through the tubes 11A and 11B can be sufficiently cooled. Therefore, the temperature efficiency is lowered.

  FIG. 8 shows a fin-tube heat exchanger of another configuration example in which the decrease in temperature efficiency due to the gap G between the adjacent fins 12 and 12 is improved. In this configuration example, in the finned tube heat exchanger shown in FIGS. 2 to 5, the gap G between adjacent fins 12 and 12 is divided by a plurality of rectifying partitions 29, and the air in the gap G is divided. Is prevented from mixing. The plurality of partitions 29 are provided side by side in the direction in which the two tubes 11A and 11B constituting the heat exchange unit 9 are separated, and are provided in parallel to the direction in which the heat exchange units 9 are arranged, that is, the path direction of the low-temperature air. ing.

  As described above, when the gap G between the adjacent fins 12 and 12 is partitioned by the partition 29, the temperature distribution of the low-temperature air can be improved as shown by hatching in FIG. Thereby, the temperature of the high temperature air flowing through the tubes 11A and 11B can be cooled to a lower temperature, and the temperature efficiency can be improved.

  FIG. 10 shows a specific example of the turbine unit 5 for air cycle refrigeration. The turbine unit 5 includes an air compressor 6 and an air expander 7, and a compressor impeller 6 a of the air compressor 6 and a turbine impeller 7 a of the air expander 7 are respectively attached to both ends of the main shaft 13. Further, the compressor impeller 6a is driven by the power generated in the turbine impeller 7a, and no other drive source is provided.

In FIG. 2, the air compressor 6 has a housing 6b facing the compressor impeller 6a via a minute gap d1, and air sucked in the axial direction from the suction port 6c in the center is received by the compressor impeller 6a. It compresses and it discharges | emits as shown by the arrow 6d from the exit (not shown) of an outer peripheral part.
The air expander 7 has a housing 7b that opposes the turbine impeller 7a with a minute gap d2, and aspirates and expands the air sucked from the outer peripheral portion as indicated by an arrow 7c by the turbine impeller 7a. It discharges in the axial direction from the discharge port 7d of the part.

  The bearing unit 4 in the turbine unit 5 supports the main shaft 13 with a plurality of bearings 15 and 16 in the radial direction, and supports the thrust force applied to the main shaft 13 with an electromagnet 17. The turbine unit 5 controls a thrust 18 acting on the main shaft 13 due to the air in the air compressor 6 and the air expander 7, and controls the bearing force by the electromagnet 17 according to the output of the sensor 18. And a controller 19. The electromagnet 17 is installed in the spindle housing 14 so as to face the both surfaces of a flange-like thrust plate 13a made of a ferromagnetic material provided at the center of the main shaft 13 without contact.

The bearings 15 and 16 that support the main shaft 13 are rolling bearings and have a function of regulating the axial position, and for example, deep groove ball bearings are used. In the case of a deep groove ball bearing, it has a thrust support function in both directions, and has the effect of returning the axial position of the inner and outer rings to the neutral position. These two bearings 15 and 16 are arranged in the vicinity of the compressor impeller 6a and the turbine impeller 7a in the spindle housing 14, respectively.
The bearing 16 on the installation side of the sensor 18 is fitted in a bearing housing 23 fitted in the spindle housing 14.

The main shaft 13 is a stepped shaft having a large-diameter portion 13b at the center and small-diameter portions 13c at both ends. The bearings 15 and 16 on both sides have their inner rings 15a and 16a fitted into the small diameter portion 13c in a press-fit state, and one of the width surfaces engages with a stepped surface between the large diameter portion 13b and the small diameter portion 13c.
The portions of the spindle housing 14 closer to the impellers 6a and 7a than the bearings 15 and 16 on both sides are formed with an inner diameter surface close to the main shaft 13, and non-contact seals 21 and 22 are formed on the inner diameter surface. Yes. The non-contact seals 21 and 22 are labyrinth seals in which a plurality of circumferential grooves are arranged in the axial direction on the inner diameter surface of the spindle housing 14.

  In the air cycle refrigeration apparatus, the turbine unit 5 having this configuration is compressed by the air compressor 6 to increase the temperature by being cooled by the air compressor 6, and is cooled by the heat dissipation heat exchanger 2 and the heat recovery heat exchanger 3. The air is used by the air expander 7 so as to be cooled and discharged by adiabatic expansion to a target temperature, for example, a very low temperature of about −30 ° C. to −60 ° C.

The turbine unit 5 has an air compressor 6 and an air expander 7 attached to a common main shaft 13 and drives the compressor impeller 6a by the power generated by the turbine impeller 7a. Cooling can be efficiently performed with a compact configuration.
In order to secure the efficiency of compression and expansion of the turbine unit 5, it is necessary to keep the gaps d1 and d2 between the impellers 6a and 7a and the housings 6b and 7b minute. In the air cycle refrigeration system, ensuring this efficiency is important. On the other hand, since the main shaft 13 is supported by rolling type bearings 15 and 16, the axial direction of the main shaft 13 is regulated to some extent by the restriction function of the axial direction position of the rolling bearing, and each impeller 6a, 7a and housing The minute gaps d1 and d2 between 6b and 7b can be kept constant.

However, a thrust force is applied to the main shaft 13 of the turbine unit 5 by the pressure of air acting on the impellers 6a and 7a. Further, in a turbine unit used in an air cooling system, the rotation speed is very high, for example, about 80,000 to 100,000 rotations per minute. Therefore, when the thrust force acts on the rolling bearings 15 and 16 that rotatably support the main shaft 13, the long-term durability of the bearings 15 and 16 decreases.
In this embodiment, since the thrust force is supported by the electromagnet 17, the thrust force acting on the rolling bearings 15 and 16 for supporting the main shaft 13 can be reduced while suppressing an increase in torque without contact. In this case, a sensor 18 for detecting a thrust force acting on the main shaft 13 by the air in the air compressor 6 and the air expander 7 and a controller for controlling the bearing force by the electromagnet 17 in accordance with the output of the sensor 18. Accordingly, the rolling bearings 15 and 16 can be used in an optimum state with respect to the thrust force according to the bearing specifications.
In particular, since the sensor 18 is arranged in the vicinity of the bearing 16, the thrust force acting on the bearing 16 in question can be directly measured, the measurement accuracy is good, and the thrust force can be precisely controlled. .

  Therefore, stable high-speed rotation of the main shaft 13 can be obtained while maintaining appropriate gaps d1 and d2 between the impellers 6a and 7a, and the long-term durability and life of the bearings 15 and 16 can be improved. Since the long-term durability of the bearings 15 and 16 is improved, the reliability of the entire air cycle refrigeration turbine unit 5 and, as a whole, the air cycle refrigeration apparatus is improved. As described above, stable high-speed rotation, long-term durability, and reliability of the main shaft bearings 15 and 16 of the turbine unit 5 that are the bottleneck of the air cycle refrigeration apparatus are improved, so that the air cycle refrigeration apparatus can be put to practical use. Become.

  FIG. 11 shows another configuration example of the turbine unit 5 in the above-described air cycle refrigeration apparatus. The turbine unit 5 is provided with a motor 90 that rotationally drives the main shaft 13 in the configuration shown in FIG. The motor 90 is provided side by side with the electromagnet 17 and includes a stator 91 provided on the spindle housing 14 and a rotor 92 provided on the main shaft 13. The stator 91 has a stator coil 91a, and the rotor 92 is made of a magnet or the like. The motor 90 is controlled by a motor controller 93.

  In the turbine unit 5, the compressor impeller 6 a is rotationally driven by the driving force of the turbine impeller 7 a generated by the air expander 7 and the driving force of the motor 90. Therefore, the air compressor 6 can be driven without adding auxiliary means for the air compressor 6, and the apparatus can be made compact.

1 is a system diagram of an air cycle refrigeration apparatus according to an embodiment of the present invention. It is a front sectional view of the fin tube type heat exchanger used for the air cycle refrigeration equipment. It is side surface sectional drawing of the fin tube type heat exchanger used for the air cycle refrigerating apparatus. It is front sectional drawing of the principal part of the fin tube type heat exchanger. It is a perspective view of the principal part of the fin tube type heat exchanger. It is a horizontal sectional view of the important section of the fin tube type heat exchanger. It is explanatory drawing of the temperature distribution of the low temperature air in the fin tube type heat exchanger. It is a horizontal sectional view of the important section of other examples of composition of the fin tube type heat exchanger. It is explanatory drawing of the temperature distribution of the low temperature air in the fin tube type heat exchanger. It is sectional drawing of the turbine unit for air cycle refrigeration used for the air cycle refrigeration equipment. It is sectional drawing of the other structural example of the turbine unit for air cycle refrigeration used for the air cycle refrigeration apparatus.

Explanation of symbols

2 ... Heat dissipation heat exchanger 3 ... Heat recovery heat exchanger 5 ... Turbine unit 6 ... Air compressor 6a ... Compressor impeller 7 ... Air expander 7a ... Turbine impeller 9 ... Heat exchange unit 10 ... Cooled part 11A , 11B ... Tube 12 ... Fin 13 ... Main shaft 15, 16 ... Bearing 17 ... Electromagnet 90 ... Motor 92 ... Motor rotor

Claims (6)

For the inflow air, air that has been subjected to compression by the air compressor of the turbine unit having an air compressor and an air expander, cooling by a heat exchanger for heat dissipation, and adiabatic expansion by the air expander of the turbine unit in order. Supplying to the cooled section, circulating the return air from the cooled section as the inflow air to the air compressor, the air path between the heat exchanger for heat radiation and the air expander, the cooled section and the air A heat recovery heat exchanger that performs heat-to-air heat exchange between the air paths between the air paths between the compressors is disposed, and the air before entering the air expander is supplied from the cooled portion. An air cycle refrigeration system for cooling with return air,
A plurality of parallel tubes that flow high-temperature air to one or both of the heat exchanger for heat dissipation and the heat exchanger for heat recovery, and between the tubes. An air cycle refrigeration apparatus using a finned tube heat exchanger in which a plurality of heat exchange units having fins provided are installed in parallel.   2. The air cycle refrigeration apparatus according to claim 1, wherein the finned tube heat exchanger is used for both the heat dissipation heat exchanger and the heat recovery heat exchanger.   3. The air cycle refrigeration apparatus according to claim 1, wherein a plurality of rectifying partitions are provided in a gap between the fins of adjacent heat exchange units arranged side by side.   In Claim 3, there are two tubes of the heat exchange unit, and a plurality of parallel heat conductive plates each provided between the two tubes and arranged in the longitudinal direction of the tubes. An air cycle refrigeration apparatus comprising fin elements arranged between heat conductive plates.   5. The power generated in the turbine impeller according to claim 1, wherein the turbine unit attaches the compressor impeller of the air compressor and the turbine impeller of the air expander to a common main shaft. An air cycle refrigeration apparatus, wherein the main shaft is rotatably supported by a bearing and a part or all of the thrust force applied to the main shaft is supported by an electromagnet. .   6. The motor rotor according to claim 1, wherein a motor rotor is attached to a common main shaft to which the compressor impeller of the air compressor and the turbine impeller of the air expander are attached. An air cycle refrigeration apparatus characterized in that the main shaft is rotated by a motor.

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