JP2009162464A - Air cycle refrigeration system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an air cycle refrigeration system carrying out cooling and heat retention of an interior of a part to be cooled from -30°C to 25°C irrespective of an environmental temperature, and preventing deterioration of efficiency even if an operating temperature becomes high. <P>SOLUTION: Temperature measuring parts T1, T2, T3 are provided for measuring a temperature of the part 1 to be cooled, an inlet temperature of the part 1, and an outside air temperature. An operation unit is provided for determining whether to cool, heat, or retain heat of the part 1 from measurement results by the temperature measuring parts T1, T2, T3. A path switching means is provided for switching flow paths in a refrigerant air passage 4 on the basis of a determination result of the operation unit. <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.

The air taken into the unit passes through the air-to-air heat exchanger, the air compressor, the water-to-air heat exchanger, and the air-to-air heat exchanger, and then enters the air expander. A technique has been proposed in which the air that has exited the air is sent to the ejector through the cold air outlet pipe from the cold air outlet port (for example, Patent Document 1).
Japanese Patent No. 2977069

  In the refrigerated container, the inside of the container needs to be cooled to -30 ° C. to 25 ° C. and kept warm regardless of the environmental temperature. In the air cycle refrigeration system, it has been difficult to construct a chilled band of 0 to 10 ° C. or a constant temperature control of 10 to 25 ° C. in the freezer. In addition, the efficiency of the air cycle refrigeration apparatus is increased when the operating temperature is −20 ° C. or lower, but the efficiency is lowered when the operating temperature is increased.

  An object of the present invention is an air cycle refrigeration capable of cooling and keeping the temperature of a cooled part from -30 ° C. to 25 ° C. regardless of the environmental temperature, and preventing a decrease in efficiency even when the operating temperature becomes high. Is to provide a device.

The air cycle refrigeration apparatus of the present invention has a refrigerant air flow path that is provided between an air inlet and an outlet of a portion to be cooled and in which a plurality of devices that respectively perform heat exchange, compression, and expansion of air are interposed, An air cycle refrigeration apparatus for cooling the air to be cooled as a refrigerant,
A temperature measurement unit that measures the temperature of the cooled part, the inlet temperature of the cooled part, and the outside air temperature is provided, and whether or not the cooled part should be cooled, heated, or kept warm from the measurement result of the temperature measuring part And a path switching means for switching the flow path in the refrigerant air flow path based on the determination result of the calculation section.

According to this configuration, the temperature of the part to be cooled, the inlet temperature, and the outside air temperature are measured by the temperature measuring unit. The calculation unit determines from the measurement result whether the cooled portion should be cooled, heated, or kept warm. The path switching means switches the flow path in the refrigerant air flow path based on the determination result of the calculation unit. This “flow path” switching is synonymous with local switching of the refrigerant air flow path, partial direction switching of the flow path, and the like. Thus, since the determination by a calculating part is performed from the measurement result by a temperature measurement part, and the flow path in a refrigerant | coolant air flow path is switched, the inside of a to-be-cooled part can be cooled and kept at a desired temperature. The measurement by the temperature measurement unit can be performed, for example, at regular intervals.
Therefore, regardless of the environmental temperature, the inside of the cooled part can be cooled to -30 ° C. or higher and 25 ° C. or lower, and the efficiency can be prevented from being lowered even when the operating temperature is increased.

In this invention, it has a turbine unit having a compressor impeller and an expansion turbine impeller attached to a main shaft, and the plurality of devices include a compressor having the compressor impeller, an expansion turbine having the turbine impeller, and heat recovery heat. There are exchangers, pre-compression means, heat exchangers for heat dissipation, and other heat exchangers for heat dissipation,
The heat recovery heat exchanger that recovers heat of the return air from the cooled part, compression by the pre-compression means, cooling by the heat dissipation heat exchanger that performs heat exchange between the outside air and compressed air, by the compressor The compression, the cooling by the other heat radiating heat exchanger, the cooling by the heat recovery heat exchanger, and the adiabatic expansion by the expansion turbine may be sequentially performed.

  According to this configuration, one refrigerant air flow path is set in the initial operation state. First, after the heat recovery heat exchanger recovers heat of the return air from the part to be cooled, it is compressed to a predetermined pressure by the pre-compression means. The air is heated by the compression, and then heat exchange between the outside air and the compressed air is performed by a heat-dissipating heat exchanger. The air cooled by this heat exchange is compressed by a compressor and heated. In this state, the air is cooled by another heat radiating heat exchanger, and further, this air is cooled by a heat recovery heat exchanger. The cooled air is adiabatically expanded and cooled by an expansion turbine, and discharged from the discharge port to the cooled portion.

  After the operation is started, the air flow order of a plurality of devices is switched or the opening and closing of the bypass channel is switched based on the determination result of the calculation unit. Thereby, it becomes possible to raise the air temperature of the flow path from the downstream of the heat exchanger for heat recovery to the upstream of the expansion turbine, or to increase the air of the flow path from the downstream of the expansion turbine to the cooled portion. .

In this invention, it has a turbine unit having a compressor impeller and an expansion turbine impeller attached to a main shaft, and the plurality of devices include a compressor having the compressor impeller, an expansion turbine having the turbine impeller, and heat recovery heat. There are exchangers and heat exchangers for heat dissipation,
The heat recovery heat exchanger that recovers heat of the return air from the cooled part, the compression by the compressor, the cooling by the heat dissipation heat exchanger that performs heat exchange between the outside air and the compressed air, and the heat recovery heat Cooling by the exchanger and adiabatic expansion by the expansion turbine may be sequentially performed.

  According to this configuration, one refrigerant air flow path is set in the initial operation state. First, after the heat exchanger for heat recovery performs heat recovery of the return air from the part to be cooled, this air is compressed by a compressor and the temperature is raised. In this state, the air is cooled by the heat-dissipating heat exchanger, and further, this air is cooled by the heat-recovery heat exchanger. The cooled air is adiabatically expanded and cooled by an expansion turbine, and discharged from the discharge port to the cooled portion. After the operation is started, the air flow order of a plurality of devices is switched or the opening and closing of the bypass channel is switched based on the determination result of the calculation unit. Thereby, it becomes possible to raise the air temperature of the path | route from the downstream of the heat exchanger for heat recovery to the upstream of an expansion turbine, or to raise the air of the path | route from the downstream of an expansion turbine to a to-be-cooled part.

  Among the refrigerant air flow paths, a bypass flow path that bypasses the cooling-side flow path of the heat recovery heat exchanger may be provided, and the path switching means may switch opening and closing of the bypass flow path. When the arithmetic unit determines that the portion to be cooled should be heated or kept warm, the outside air is introduced by opening the bypass channel. As a result, the air downstream of the cooling side path in the heat recovery heat exchanger is not cooled to the cooling temperature before the bypass flow path is opened. In this way, the air temperature in the middle of the refrigerant air flow path can be adjusted by opening the bypass flow path, and cooling or heat retention in the cooled portion can be made possible.

  Of the refrigerant air flow path, a bypass flow path that bypasses the expansion turbine may be provided, and the path switching means may switch opening and closing of the bypass flow path. When the arithmetic unit determines that the part to be cooled is to be heated or kept warm, as a result of the outside air being introduced by opening the bypass channel, the air reaching the outlet is not cooled to the cooling temperature before the bypass channel is opened. . Therefore, it is possible to cool or keep the inside of the cooled part.

  You may provide the refrigerant | coolant flow control means which controls the refrigerant | coolant flow rate of the said heat exchanger for thermal radiation based on the determination result of the said calculating part. A refrigerant | coolant flow control means controls the output setting part of the heat exchanger for thermal radiation based on the determination result of a calculating part. Thereby, it becomes possible to adjust the refrigerant | coolant flow rate of the heat exchanger for thermal radiation, and to finely adjust the temperature of the air guide | induced to a to-be-cooled part.

  The turbine unit may include a motor that rotationally drives the main shaft, and motor rotation speed control means that controls the rotation speed of the motor based on the determination result of the calculation unit may be provided. If the rotational speed of the motor is controlled based on the determination result of the calculation unit, the temperature gradient of the air downstream of the expansion turbine can be changed. When the motor rotation speed is controlled to be high by the motor rotation speed control means, the temperature gradient becomes large and the air temperature reaching the cooled part can be lowered more actively. When the motor rotation speed is controlled to be low by the motor rotation speed control means, the temperature gradient can be reduced and the air temperature reaching the cooled portion can be prevented from becoming too low.

  The turbine unit uses a rolling bearing and a magnetic bearing in combination, the rolling bearing supports a radial load, the magnetic bearing supports one or both of an axial load and a bearing preload, and constitutes the electromagnet constituting the magnetic bearing. May be a magnetic bearing device attached to the spindle housing so as to face a flange-like thrust plate made of a ferromagnetic material provided on the main shaft without contact.

  According to this configuration, since the rolling bearing and the magnetic bearing are used in combination, the rolling bearing supports the radial load, and the magnetic bearing supports one or both of the axial load and the bearing preload. The long-term durability of the rolling bearing can be ensured, and damage when the power supply is stopped when only the magnetic bearing is supported can be avoided. In addition, since the permanent magnet of the motor rotor is provided on the flange-shaped thrust plate facing the electromagnet of the magnetic bearing, the spindle length is shortened by the combined use of the thrust plate of the magnetic bearing and the motor rotor. The decrease in the number can be avoided and the rotation with low vibration at the time of high-speed rotation is possible.

  The turbine unit includes a motor that rotationally drives a main shaft. A motor rotor of the motor is provided on a main shaft common to the thrust plate, and a motor stator is disposed so as to face the motor rotor, and the motor rotor is disposed between the motor rotor and the motor stator. It may be a motor-integrated bearing device that rotates the main shaft by the magnetic force or Lorentz force. As described above, the motor rotor is provided on the same main shaft as the thrust plate, and the motor stator is disposed so as to face the motor rotor, so that the structure of the apparatus can be simplified.

The air cycle refrigeration apparatus of the present invention has a refrigerant air flow path that is provided between an air inlet and an outlet of a portion to be cooled and in which a plurality of devices that respectively perform heat exchange, compression, and expansion of air are interposed, An air cycle refrigeration apparatus for cooling the air to be cooled as a refrigerant,
A temperature measurement unit that measures the temperature of the cooled part, the inlet temperature of the cooled part, and the outside air temperature is provided, and whether or not the cooled part should be cooled, heated, or kept warm from the measurement result of the temperature measuring part And a path switching means for switching the flow path in the refrigerant air flow path based on the determination result of the calculation section is provided. Cooling to below ℃ and heat insulation are possible, and even if the operating temperature becomes high, efficiency reduction can be prevented.

A first embodiment of the present invention will be described with reference to FIGS.
FIG. 1 shows the overall configuration of an air cycle refrigeration apparatus. This air cycle refrigeration apparatus is an apparatus that directly cools the air of the cooled part 1 as a refrigerant, such as a freezer, and has a refrigerant air flow path from the air intake port 2 to the discharge port 3 respectively opened in the cooled part 1. 4. The refrigerant air flow path 4 includes a pre-compression means 5, a first heat dissipation heat exchanger 6, a compressor 8 of an air cycle refrigeration cooling turbine unit 7, and a second heat dissipation heat exchanger 9. The heat recovery heat exchanger 10 and the expansion turbine 11 of the turbine unit 7 are provided in this order. Temperature sensors T1, T2, and T3 are provided as temperature measuring units for measuring the temperature in the cooled portion 1, the temperature in the flow path from the expansion turbine 11 to the cooled portion 1, and the outside air temperature.

  As shown in FIG. 2, the motor-integrated magnetic bearing device in the turbine unit 7 supports the main shaft 12 with a plurality of rolling bearings 13 and 14 in the radial direction, and either the axial load or the bearing preload applied to the main shaft 12. One or both of them are supported by an electromagnet 15 and a permanent magnet 16 as magnetic bearings, respectively, and a motor 17 for rotating the main shaft 12 is provided. As will be described later, the controller 18, which is a control means, controls the number of rotations of the motor 17 based on the determination result of the calculation unit 19 (FIG. 3).

  As shown in FIG. 1, the pre-compression means 5 comprises a blower or the like, and is driven by a motor 5a as a power unit. The first heat-dissipating heat exchanger 6 and the second heat-dissipating heat exchanger 9 have heat exchangers 6a and 9a for circulating the cooling medium, respectively, and the cooling medium and the refrigerant in the heat exchangers 6a and 9a. Heat exchange is performed with the air in the air flow path 4. Each heat exchanger 6a (9a) is connected to a blower 6b (9b) and a pump 6c (9c) by piping, and a cooling medium heated by heat exchange is supplied by the blower 6b (9b) and the pump 6c (9c). To be cooled. The controller 18 can switch the blower 6b (9b) and the pump 6c (9c) on and off based on the determination result of the calculation unit 19. Further, the blower 6b (9b) and the pump 6c (9c) are configured so that the refrigerant flow rate can be adjusted. That is, the controller 18 controls the output setting unit 20 (FIG. 3) of the drive source of the blower 6b (9b) and the pump 6c (9c) based on the determination result of the calculation unit 19. Thereby, the refrigerant | coolant flow rate of the heat exchanger 6 (9) for thermal radiation can be adjusted.

  A bypass passage 21 for bypassing the cooling-side passage 10a of the heat recovery heat exchanger 10 is provided, and a first valve 22 as a device is interposed in the middle of the bypass passage 21. The first valve 22 can be opened and closed and the opening degree can be adjusted. The opening and closing of the first valve 22 is switched according to the determination of the calculation unit 19 described later. In the initial state, the first valve 22 is set in a closed state. In the state where the first valve 22 is closed, the bypass flow path 21 is closed, and the air is cooled to a predetermined temperature according to the temperature of the cooled part 1. When the bypass passage 21 is opened in a state where the first valve 22 is opened, heat exchange cannot be performed in the heat recovery heat exchanger 10, and the air reaching the expansion turbine 11 is not transferred to the heat dissipation heat exchanger 9. Refrigerant temperature is within + 10 ° C.

  Further, a bypass passage 23 for bypassing the expansion turbine 11 of the turbine unit 7 is provided, and a second valve 24 is interposed in the middle of the bypass passage 23. The second valve 24 can be opened and closed and the opening degree can be adjusted. Depending on the determination of the calculation unit 19, the opening and closing of the second valve 24 is switched. In the initial operation state, the second valve 24 is set in a closed state. In the state where the second valve 24 is closed, the bypass flow path 23 is closed, and the air is cooled to, for example, −40 ° C. to −30 ° C. by the expansion turbine 11. If the bypass flow path 23 is opened in a state where the second valve 24 is opened, adiabatic expansion cannot be performed in the expander, and the air reaching the discharge port 3 is not cooled.

  This air cycle refrigeration system is a system that keeps the cooled part 1 at, for example, about 0 ° C. to −60 ° C., from the outlet 1 a of the cooled part 1 to the intake 2 of the refrigerant air flow path 4. About 1 atmosphere of air flows in. Note that the numerical values of temperature and atmospheric pressure shown below are examples that serve as a guide. In the initial operation state, the air flowing into the intake port 2 is used for cooling the air in the refrigerant air flow path 4 by the heat recovery heat exchanger 10 and is heated to 40 ° C. The heated air remains at 1 atm, but is compressed to 1.4 atm by the pre-compression means 5, and the temperature is raised to 70 ° C. by the compression. The first heat radiating heat exchanger 6 cools the heated air at 70 ° C. to, for example, 40 ° C. by the blower 6b and the pump 6c.

The air at 40 ° C. and 1.4 atm cooled by the heat exchange is compressed to 1.8 atm by the compressor 8 of the turbine unit 7, and is heated to about 70 ° C. by this compression. It is cooled to 40 ° C. by the heat exchanger 9 for use. The 40 ° C. air is cooled to −20 ° C. or less by the −30 ° C. air in the heat recovery heat exchanger 10. The atmospheric pressure is maintained at 1.8 atmospheric pressure discharged from the compressor 8.
The air cooled to −20 ° C. or lower by the heat recovery heat exchanger 10 is adiabatically expanded by the expansion turbine 11 of the turbine unit 7, cooled to −55 ° C., and discharged from the discharge port 3 to the inlet 1 b of the cooled portion 1. Discharged.

  As shown in FIG. 2, the compressor 8 has a housing 8b facing the compressor impeller 8a with a small gap, and the air sucked in the axial direction from the suction port 8c in the center is received by the compressor impeller 8a. It compresses and discharges as shown by the arrow 8d from the exit (not shown) of an outer peripheral part. The expansion turbine 11 has a turbine housing 11b opposed to the turbine impeller 11a through a minute gap, and the air sucked from the outer peripheral portion as indicated by an arrow 11c is adiabatically expanded by the turbine impeller 11a, and the center portion Is discharged in the axial direction from the discharge port 11d.

  In the turbine unit 7, the main shaft 12 is supported by a plurality of bearings 13 and 14 in the radial direction, and the thrust force applied to the main shaft 12 is supported by an electromagnet 15. The electromagnet 15 is installed in the spindle housing 25 so as to face the both surfaces of a flange-like thrust plate 12a made of a ferromagnetic material provided at the center of the main shaft 12 without contact. The turbine unit 7 is provided with a motor 17 that rotationally drives the main shaft 12. The motor 17 is provided side by side with the electromagnet 15 and includes a stator 26 provided on the spindle housing 25 and a rotor 27 provided on the main shaft 12. The stator 26 has a stator coil 26a, and the rotor 27 is made of a magnet or the like. The motor 17 is controlled by the controller 18.

  The bearings 13 and 14 that support the main shaft 12 are rolling bearings and have a function of restricting the position in the axial direction. 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 13 and 14 are arranged in the vicinity of the compressor impeller 8a and the turbine impeller 11a in the spindle housing 25, respectively. The bearing 14 is fitted in a bearing housing fitted in the spindle housing 25.

The main shaft 12 is a stepped shaft having a large-diameter portion 12b at the center and small-diameter portions 12c at both ends. The inner rings of the bearings 13 and 14 on both sides are fitted into the small diameter portion 12c in a press-fitted state, and one width surface is engaged with the step surface between the large diameter portion 12b and the small diameter portion 12c.
A portion of the spindle housing 25 closer to each impeller 8a, 11a than the bearings 13, 14 on both sides is formed with an inner diameter surface close to the main shaft 12, and non-contact seals 28, 29 are formed on the inner diameter surface. Yes. The non-contact seals 28 and 29 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 25.

The electrical configuration of the air cycle refrigeration apparatus will be described.
As shown in FIG. 3, the controller 18 that is a control unit includes a calculation unit 19, drive units 30 and 31, a motor drive circuit 32, and an output setting unit 20. The computing unit 19 is realized by, for example, a central processing unit (abbreviated as CPU: Central Processing Unit). The calculation unit 19 determines whether or not the cooled part 1 should be cooled, heated, or kept warm based on output signals from the temperature sensors T1 to T3. In a storage unit (not shown), a predetermined set temperature of the outside air temperature, a set temperature in the cooled part 1 and a set temperature of the inlet 1b of the cooled part 1 are stored in a rewritable manner.
When the output signals from the temperature sensors T1, T2, and T3 are input to the arithmetic unit 19 at regular time intervals or whenever there is a temperature change, the controller 18 determines in light of the set temperature stored in the storage unit. Is executed by the arithmetic unit 19.

The arithmetic unit 19 includes a valve control unit 19a for controlling the opening and closing of the first and second valves 22 and 24, a refrigerant flow control unit 19b for controlling on / off of the pump 6c (9c), a refrigerant flow rate, and the like. Motor rotation speed control means 19c for controlling the rotation speed of the motor 17 is provided.
In the arithmetic unit 19, the first valve 22 is electrically connected to the valve control means 19a via a drive unit 30 that amplifies the first valve 22 to a necessary and sufficient drive voltage. The second valve 24 is electrically connected to the valve control means 19a via a drive unit 31 that amplifies the second valve 24 to a necessary and sufficient drive voltage. These drive units 30 and 31 are realized by, for example, an amplifier or a relay. Further, in the calculation unit 19, the motor stator 26 is electrically connected to the motor rotation speed control means 19 c through the motor drive circuit 32, and the pump 6 c (9 c) is driven through the output setting unit 20. The source is electrically connected. These valve control means 19a, refrigerant flow rate control means 19b, and motor rotation speed control means 19c correspond to the path switching means.

表１は、温度指令と、バルブ等の開閉状態との関係を示す表である。
運転初期状態つまり冷凍モードにおいては、バルブ制御手段１９ａにより第１のバルブ２２「閉」、第２のバルブ２４「閉」、モータ回転数制御手段１９ｃによりモータ１７の回転数「高」、冷媒流量制御手段１９ｂにより各ブロワ／ポンプ「オン」に設定されている。この運転初期状態では、第１のバルブ２２「閉」によりそのバイパス経路２１が閉じられ、被冷却部１の現温度に応じて熱回収用熱交換器１０により空気を所定温度まで冷却する。また、第２のバルブ２４「閉」によりそのバイパス経路２３が閉じられ、さらにモータ１７の回転数「高」により空気が−４０℃〜−３０℃まで冷却される。このモータ１７の回転数「高」の場合、冷却する空気の温度勾配が最も大きくなる。

Table 1 is a table showing the relationship between the temperature command and the open / close state of a valve or the like.
In the initial operation state, that is, in the refrigerating mode, the first valve 22 is “closed” and the second valve 24 is “closed” by the valve control means 19a, the rotational speed “high” of the motor 17 by the motor rotational speed control means 19c, and the refrigerant flow rate. Each blower / pump is set to “on” by the control means 19b. In this initial operation state, the bypass valve 21 is closed by the first valve 22 “closed”, and the air is cooled to a predetermined temperature by the heat recovery heat exchanger 10 according to the current temperature of the cooled part 1. Further, the bypass path 23 is closed by the second valve 24 “closed”, and the air is further cooled to −40 ° C. to −30 ° C. by the rotational speed “high” of the motor 17. When the rotation speed of the motor 17 is “high”, the temperature gradient of the air to be cooled becomes the largest.

  Here, the rotation speed “high” of the motor 17 is, for example, 60000 rpm or more, the rotation speed “medium” of the motor 17 is, for example, 20000 rpm or more and 40000 rpm or less, and the rotation speed “low” of the motor 17 is, for example, 10000 rpm or more and less than 20000 rpm. . However, these rotational speeds are changed according to the refrigeration capacity of the air cycle refrigeration apparatus, and are not necessarily limited to these rotational speeds.

  When the outside air temperature is higher than a predetermined set temperature and the temperature in the cooled part 1 is lower than the predetermined set temperature, the calculation unit 19 determines that the cooled part 1 should be cooled. Thus, the controller 18 uses the valve control means 19a to “close” the first valve 22 and the second valve 24 to “close”, the motor speed control means 19c to “rotate” the motor 17 “low”, and the refrigerant flow control means. 19b controls each blower / pump "on". This state is an ideal state with the lowest power consumption. In this state, the bypass valve 21 is closed by the first valve 22 “closed”, and the air is cooled to a predetermined temperature by the heat recovery heat exchanger 10 according to the current temperature of the cooled part 1. The bypass valve 23 is closed by the second valve 24 “closed”, and the air is cooled several times by the rotation speed “low” of the motor 17. When the rotation speed of the motor 17 is “low”, the temperature gradient of the air to be cooled becomes the smallest.

  When the outside air temperature is lower than the predetermined set temperature and the temperature in the cooled part 1 is higher than the predetermined set temperature, the calculation unit 19 determines that the cooled part 1 should be heated or kept warm. Thereby, the controller 18 controls the first valve 22 “open”, the second valve 24 “closed”, the rotation speed “medium” of the motor 17, and each blower / pump “on”. In this state, the bypass valve 21 is opened by the first valve 22 “opened”, and the air reaching the expansion turbine 11 falls within the refrigerant temperature + 10 ° C. of the heat exchanger 9 for heat radiation. The bypass valve 23 is closed by the second valve 24 “closed”, and the air is cooled by the adiabatic expansion of the expander 11 by the rotational speed “medium” of the motor 17. When the rotation speed of the motor 17 is “medium”, the temperature gradient of the air to be cooled is larger than the “low” temperature gradient and smaller than the “high” temperature gradient.

  When the outside air temperature is lower than the predetermined set temperature and the temperature in the cooled part 1 is lower than the predetermined set temperature, the calculation unit 19 determines that the cooled part 1 should be heated or kept warm. Thus, the controller 18 controls the first valve 22 “open”, the second valve 24 “open”, the rotation speed “medium” of the motor 17, and each blower / pump “off”. In this state, the bypass valve 21 is opened by the first valve 22 “opened”, and the air reaching the expansion turbine 11 falls within the refrigerant temperature + 10 ° C. of the heat exchanger 9 for heat radiation. When the bypass flow path 23 is opened by the second valve 24 “open”, the adiabatic expansion cannot be performed in the expander, and the cooling temperature of the air from the discharge port 3 to the inlet 1b of the cooled portion 1 is suppressed. The Further, the refrigerant air heated by the rotation speed “medium” of the motor 17 is circulated.

  According to the air cycle refrigeration apparatus according to the first embodiment described above, the calculation unit 19 is cooled in light of the set temperature stored in the storage unit based on the output signals from the temperature sensors T1, T2, and T3. It is determined whether the part 1 should be cooled, heated, or kept warm. Based on the determination result of the calculation unit 19, as shown in Table 1 above, the open / close state of the first and second valves 22 and 24, the rotation speed of the motor 17, and the ON / OFF of each blower / pump are controlled. To do. In this way, the calculation unit 19 makes a determination from the measurement results of the temperature sensors T1, T2, and T3 to control the motor 17 and the blower / pump drive source with large power consumption, and to control the opening and closing of the bypass channels 21 and 23. It is carried out. For this reason, the inside of the cooled part 1 can be cooled to -30 ° C. or higher and 25 ° C. or lower regardless of the environmental temperature, and the efficiency can be prevented from being lowered even when the operating temperature becomes high. Even in a setting where the operating temperature in the section 1 is high, the power consumption can be reduced as compared with the conventional technique.

  Since the bypass flow path 21 that bypasses the cooling-side flow path 10a of the heat recovery heat exchanger 10 is provided in the refrigerant air flow path 4, the arithmetic unit 19 determines that the cooled portion 1 should be heated or kept warm. The bypass channel 21 is opened. As a result, the air downstream of the cooling side passage 10a in the heat recovery heat exchanger 10 is not cooled to the cooling temperature before the bypass passage is opened. As described above, the air temperature in the refrigerant air flow path 4 can be adjusted by opening the bypass flow path 21 to enable cooling or heat retention in the cooled portion 1.

  Since the bypass flow path 23 that bypasses the expansion turbine 11 is provided in the refrigerant air flow path 4, if the calculation unit 19 determines that the cooled part 1 should be heated or kept warm, the bypass flow path 23 is opened and expanded. Stop adiabatic expansion in the machine. As a result, the air reaching the discharge port 3 is not cooled to the cooling temperature before the bypass passage is opened. Therefore, cooling or heat retention in the cooled part 1 can be enabled.

The turbine unit 7 includes a motor 17 that rotationally drives the main shaft 12, and the controller 18 controls the rotational speed of the motor 17 based on the determination result of the calculation unit 19. When the rotational speed of the motor 17 is controlled with the bypass passage 23 closed, the temperature gradient of the air downstream of the compressor 8, the temperature gradient of the air downstream of the expansion turbine 11, and the flow rate of the refrigerant air can be changed. it can. When the rotation speed of the motor 17 is controlled to be “high” by the controller 18, the temperature gradient of the air to be cooled becomes the largest. Therefore, the air temperature reaching the inlet 1b of the cooled part 1 can be lowered more actively. When the rotation speed of the motor 17 is controlled to “medium” by the controller 18, the temperature gradient of the cooling air is larger than the temperature gradient of the rotation speed “low” and smaller than the temperature gradient of the rotation speed “high”.
When the rotation speed of the motor 17 is controlled to be “low” by the controller 18, the temperature gradient of the air to be cooled becomes the smallest. Thereby, it is possible to prevent the air temperature reaching the inlet of the cooled portion 1 from becoming too low. In addition, the power consumption of the motor 17 can be reduced. When the rotational speed of the motor 17 is controlled in a state where the bypass passage 23 is opened, the temperature gradient of the air downstream of the compressor 8 and the flow rate of the refrigerant air can be changed.

  The turbine unit 7 uses rolling bearings 13 and 14 in combination with a magnetic bearing, the rolling bearings 13 and 14 support a radial load, and the magnetic bearing supports an axial load and / or a bearing preload. Therefore, accurate support in the axial direction can be performed, long-term durability of the rolling bearings 13 and 14 can be ensured, and damage when the power supply is stopped when only the magnetic bearing is supported can be avoided. Further, when the permanent magnet of the motor rotor is provided on the flange-shaped thrust plate 12a opposed to the electromagnet 15 of the magnetic bearing, the spindle length is shortened by the combined use of the thrust plate 12a of the magnetic bearing and the motor rotor. At the same time, it is possible to avoid a decrease in the natural frequency and to rotate with low vibration during high-speed rotation.

  A motor rotor 27 of a motor 17 that rotationally drives the main shaft 12 is provided on the main shaft 12 common to the thrust plate 12 a, and a motor stator 26 is disposed so as to face the motor rotor 27, and the motor rotor 27 and the motor stator 26 are connected to each other. A motor-integrated bearing device that rotates the main shaft 12 by a magnetic force or Lorentz force therebetween may be provided. Thus, when the motor rotor 27 is provided on the main shaft 12 common to the thrust plate 12 a and the motor stator 26 is disposed so as to face the motor rotor 27, the device structure can be simplified.

Next, a second embodiment of the present invention will be described with reference to FIG.
In the following description, the same reference numerals are given to portions corresponding to the matters described in the preceding forms in each embodiment, and overlapping description may be omitted. When only a part of the configuration is described, the other parts of the configuration are the same as those described in the preceding section. Not only the combination of the parts specifically described in each embodiment, but also the embodiments can be partially combined as long as the combination does not hinder.

In the air cycle refrigeration apparatus according to the second embodiment, the refrigerant air flow path 4 includes a compressor 8 of the turbine unit 7, an expansion turbine 11, a heat recovery heat exchanger 10, and heat dissipation heat exchange as a plurality of devices. A container 9 and first and second valves 22 and 24 are provided. In addition, temperature sensors T1, T2, and T3 are provided as temperature measuring units for measuring the temperature in the cooled part 1, the temperature in the flow path from the expansion turbine 11 to the cooled part 1, and the outside air temperature.
In addition, the controller 18 of the air cycle refrigeration apparatus has the same configuration as the block diagram shown in FIG. 3 described above, and the relationship between the temperature command and the open / closed state of the valves and the like is the same as in Table 1 above. It has become.

  In this air cycle refrigeration apparatus, air flows from the outlet 1 a of the cooled part 1 into the inlet 2 of the refrigerant air flow path 4. In the initial operation state, the air that has flowed into the intake port 2 is used for cooling the air in the refrigerant air flow path 4 by the heat recovery heat exchanger 10 and is heated. The heated air is compressed by the compressor 8 and is cooled by the heat-dissipating heat exchanger 9 while being heated by the compression. The cooled air is cooled by the heat recovery heat exchanger 10. As for the atmospheric pressure, the atmospheric pressure discharged from the compressor 8 is maintained. The air cooled by the heat recovery heat exchanger 10 is adiabatically expanded by the expansion turbine 11 of the turbine unit 7, cooled, and discharged from the discharge port 3 to the inlet 1 b of the cooled portion 1.

  According to the air cycle refrigeration apparatus according to the second embodiment, the pre-compression means and the first heat radiation heat exchanger can be omitted as compared with the air cycle refrigeration apparatus of FIG. Accordingly, the number of parts of the device can be reduced, the structure can be simplified, and the manufacturing cost can be reduced. Further, since the structure can be simplified, the apparatus can be miniaturized and the versatility of attachment to containers of various sizes can be improved. In addition, the same operations and effects as in the first embodiment are exhibited.

As another embodiment of the present invention, the controller 18 may switch the opening / closing of each valve and adjust the opening of each valve according to the determination of the calculation unit 19. If the opening degree of the first valve 22 can be adjusted according to the determination of the calculation unit 19, the ratio between the amount of air exchanged by the heat recovery heat exchanger 10 and the amount of air passing through the bypass passage 21. Can be finely adjusted, and the temperature of the air reaching the expansion turbine 11 can be raised to a desired temperature. If the opening degree of the second valve 24 can be adjusted according to the determination of the calculation unit 19, the ratio between the amount of air adiabatically expanded by the expander 11 and the amount of air passing through the bypass flow path 23 is finely adjusted. The temperature gradient for cooling can be finely adjusted.
In this embodiment, the opening degree of one of the first and second valves 22 and 24 is adjusted by the controller 18 in accordance with the determination of the calculation unit 19, and the opening degree of either one is manually adjusted. May be. Of course, the opening degree of both the first and second valves 22 and 24 may be adjusted by the controller 18 according to the determination of the calculation unit 19.

In the first and second embodiments, only one of the first and second valves 22 and 24 may be provided. In this case, the number of parts can be reduced as compared with the first and second embodiments, and the structure can be simplified. Thereby, the manufacturing cost can be reduced.
In the first and second embodiments, the motor 17 and the drive source of the blower / pump are controlled and the opening and closing control of the bypass flow path is performed. However, as another embodiment of the present invention, the arithmetic unit 19 Based on the determination result, only the opening / closing control of the bypass channel may be performed. In this case, the processing load on the arithmetic unit 19 can be reduced, and the manufacturing cost can be reduced by simplifying the control system.
As another embodiment, at least one of the control of the motor 17, the drive source of the blower / pump, and the opening / closing control of the bypass flow path may be performed based on the determination result of the calculation unit 19. good. In this case as well, the processing load on the arithmetic unit 19 can be reduced, and the control system can be simplified to reduce the manufacturing cost.

  As another embodiment of the present invention, the controller 18 may control the on / off of the blower and the pump and control the refrigerant flow rate based on the determination result of the calculation unit 19. That is, the controller 18 controls the output setting unit 20 of the drive source of the blower and the pump based on the determination result of the calculation unit 19. Thereby, the refrigerant | coolant flow rate of the heat exchanger for thermal radiation can be adjusted. Thereby, it becomes possible to adjust more finely the temperature of the air conveyed downstream of the heat exchanger for heat radiation in the refrigerant air flow path. In this embodiment, one of the first and second heat radiating heat exchangers 6 and 9 is controlled to adjust the refrigerant flow rate based on the determination result of the calculation unit 19, and either one of the refrigerants The flow rate may be manually adjusted.

1 is a system diagram of an air cycle refrigeration apparatus according to a first embodiment of the present invention. It is sectional drawing of the turbine unit of the same air cycle refrigeration equipment. It is a block diagram showing an example of the controller of the same air cycle refrigerating device. It is a systematic diagram of the air cycle refrigeration apparatus concerning the 2nd Embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Cooled part 1a ... Outlet 1b ... Inlet 5 ... Precompression means 6 ... 1st heat radiation heat exchanger 7 ... Turbine unit 8 ... Compressor 8a ... Compressor impeller 9 ... 2nd heat radiation heat exchanger 10 ... Heat recovery heat exchanger 11 ... expansion turbine 11a ... turbine impeller 12 ... main shaft 12a ... thrust plate 13,14 ... rolling bearing 15 ... electromagnet 16 ... permanent magnet 17 ... motor 18 ... controller 19 ... calculation unit 19a ... valve control means 19b: Refrigerant flow rate control means 19c ... Motor rotation speed control means 21, 23 ... Bypass passages 22, 24 ... First and second valves 26 ... Rotor 27 ... Stator

Claims (9)

It has a refrigerant air flow path that is provided between the air inlet and outlet of the part to be cooled and interposes a plurality of devices that respectively perform heat exchange, compression, and expansion of the air, and cools the air in the part to be cooled as a refrigerant An air cycle refrigeration apparatus that performs
A temperature measurement unit that measures the temperature of the cooled part, the inlet temperature of the cooled part, and the outside air temperature is provided, and whether or not the cooled part should be cooled, heated, or kept warm from the measurement result of the temperature measuring part A calculation unit for determining
An air cycle refrigeration apparatus comprising a path switching means for switching a flow path in the refrigerant air flow path based on a determination result of the calculation unit. 2. The turbine unit according to claim 1, comprising a turbine unit having a compressor impeller and an expansion turbine impeller attached to a main shaft, wherein the plurality of devices include a compressor having the compressor impeller, an expansion turbine having the turbine impeller, and heat recovery. There are heat exchanger, pre-compression means, heat exchanger for heat dissipation, and other heat exchanger for heat dissipation,
The heat recovery heat exchanger that recovers heat of the return air from the cooled part, compression by the pre-compression means, cooling by the heat dissipation heat exchanger that performs heat exchange between the outside air and compressed air, by the compressor Compression, cooling by the other heat dissipation heat exchanger, cooling by the heat recovery heat exchanger, adiabatic expansion by the expansion turbine,
An air cycle refrigeration system that sequentially performs. 2. The turbine unit according to claim 1, comprising a turbine unit having a compressor impeller and an expansion turbine impeller attached to a main shaft, wherein the plurality of devices include a compressor having the compressor impeller, an expansion turbine having the turbine impeller, and heat recovery. There are heat exchangers and heat exchangers for heat dissipation,
The heat recovery heat exchanger that recovers heat of the return air from the cooled part, the compression by the compressor, the cooling by the heat dissipation heat exchanger that performs heat exchange between the outside air and the compressed air, and the heat recovery heat Cooling by an exchanger, adiabatic expansion by the expansion turbine,
An air cycle refrigeration system that sequentially performs.   4. The bypass flow path for bypassing the cooling side flow path of the heat recovery heat exchanger in the refrigerant air flow path according to claim 2, wherein the path switching means opens and closes the bypass flow path. Switching air cycle refrigeration equipment.   5. The air cycle according to claim 2, wherein a bypass flow path that bypasses the expansion turbine is provided in the refrigerant air flow path, and the path switching unit switches opening and closing of the bypass flow path. Refrigeration equipment.   6. The air cycle refrigeration apparatus according to claim 2, further comprising: a refrigerant flow rate control unit configured to control a refrigerant flow rate of the heat dissipation heat exchanger based on a determination result of the calculation unit.   7. The motor rotational speed control means according to claim 2, wherein the turbine unit includes a motor that rotationally drives the main shaft, and the rotational speed of the motor is controlled based on a determination result of the arithmetic unit. Air cycle refrigeration equipment provided.   8. The turbine unit according to claim 2, wherein the turbine unit uses a rolling bearing and a magnetic bearing together, the rolling bearing supports a radial load, and the magnetic bearing is either an axial load or a bearing preload. An electromagnet that supports one or both of them and that constitutes the magnetic bearing is a magnetic bearing device attached to the spindle housing so as to face a flange-like thrust plate made of a ferromagnetic material provided on the main shaft in a non-contact manner. Air cycle refrigeration equipment.   9. The turbine unit according to claim 8, wherein the turbine unit includes a motor that rotationally drives a main shaft, the motor rotor of the motor is provided on the main shaft that is common to the thrust plate, and a motor stator is disposed so as to face the motor rotor. An air cycle refrigeration apparatus, which is a motor-integrated bearing bearing apparatus that rotates a main shaft by magnetic force or Lorentz force between a motor stator.

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