JP2010048446A - Hybrid air cycle refrigerating and cooling unit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hybrid air cycle refrigerating and cooling unit improving system efficiency. <P>SOLUTION: The hybrid air cycle refrigerating and cooling unit is formed by combining an air cycle refrigerating and cooling unit 9 and a heat drive type cooling unit 10. The air cycle refrigerating and cooling unit 9 includes a compressor-turbine unit 5 formed by combining a compressor 6 and an expansion turbine 7 and with heat exchangers 2, 3. The air cycle refrigerating and cooling unit 9 performs compression by the compressor 6, cooling by the heat exchangers 2, 3 and adiabatic expansion by the expansion turbine 7 with respect to refrigerant air made to flow in from a cooled part R to cool the refrigerant air and returns it to inside of the cooled part R. The heat drive type cooling unit 10 uses waste heat of the refrigerant air of which temperature becomes high after it is made to flow out of the compressor 6. Part of the refrigerant air made to flow in from the cooled part R is cooled by the cooling unit 10 and is returned to inside of the cooled part R. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a hybrid air cycle refrigeration cooling unit configured by combining an air cycle refrigeration cooling unit and another cooling unit.

  Since the air cycle refrigeration / cooling unit uses air as a refrigerant, energy efficiency is insufficient as compared with the case where chlorofluorocarbon, ammonia gas, or the like is used. Also, 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 units are proposed for such applications. (For example, Patent Document 1).

  Further, it is known that the theoretical efficiency of air cooling is equal to or higher than that of Freon or ammonia gas in a deep coal region of -30 ° C to -60 ° C. However, it is stated that obtaining the above-described theoretical efficiency of air cooling can only be achieved with optimally designed peripheral devices. The peripheral device is a compressor, an expansion turbine, or the like.

The air cycle refrigeration cooling unit obtains high-temperature air when compressing the refrigerant air. Conventionally, this high-temperature air exchanges heat with cooling air or refrigerant by a heat-dissipating heat exchanger at the subsequent stage, and releases waste heat to the outside air. Also, as examples of waste heat utilization, hot water is obtained using water as the cooling medium of the heat-dissipating heat exchanger, and the moisture absorber is dried with the outside air that has become a high temperature by exchanging heat with the outside air. (Patent Document 2).
Japanese Patent No. 2623202 JP 2000-257968 A JP-A-9-264633

  However, as disclosed in Patent Document 2, in the example in which the waste heat of the air cycle refrigeration cooling unit is used for drying the moisture absorber, only a slight improvement in system efficiency can be achieved, especially in the air conditioning region of 10 ° C to 30 ° C. It is difficult to obtain performance equivalent to or better than that of ammonia gas.

  An object of the present invention is to provide a hybrid air cycle refrigeration cooling unit capable of improving system efficiency.

The hybrid air cycle refrigeration cooling unit of the present invention includes a compressor / turbine unit comprising a combination of a compressor and an expansion turbine, and a heat exchanger, and compresses the refrigerant air flowing in from the cooled portion by the compressor and exchanges the heat. In an air cycle refrigeration cooling unit that performs cooling by a cooler and adiabatic expansion by the expansion turbine, thereby returning the cooled refrigerant air into the cooled part,
A heat-driven cooling unit that uses the waste heat of the refrigerant air that has been discharged from the compressor and that has become hot is provided, and this cooling unit cools a part of the refrigerant air that flows from the cooled part to enter the cooled part. It is characterized by being returned.
According to this configuration, a part of the refrigerant air that flows from the cooled part is operated by operating the heat-driven cooling unit by using the waste heat of the refrigerant air that has been heated from the compressor of the air cycle refrigeration cooling unit. Since the air is cooled and returned to the part to be cooled, the system efficiency can be improved as compared with the case where the air cycle refrigeration cooling unit is operated alone.

  In the present invention, the heat-driven cooling unit includes an adsorption / regenerator filled with an adsorbent that adsorbs / desorbs vapor of the refrigerant liquid, a condenser that condenses the vapor desorbed from the adsorbent, And an evaporator for supplying the adsorbed / regenerator with the vaporized refrigerant liquid, wherein the evaporator cools the refrigerant air flowing from the cooled portion with the refrigerant liquid, and In the regenerator, the adsorbent may be dried with waste heat of the refrigerant air discharged from the compressor to desorb the vapor of the refrigerant liquid from the adsorbent.

  In the present invention, the heat-driven cooling unit includes an absorber that stores the vapor absorbing liquid and absorbs the vapor of the refrigerant liquid, a regenerator that releases the vapor of the refrigerant liquid from the vapor absorbing liquid, and the vapor absorbing liquid. An absorption cooling unit comprising a condenser for condensing the vapor of the discharged refrigerant liquid and an evaporator for evaporating the condensed refrigerant liquid and supplying the condensed refrigerant liquid to the absorber, wherein the evaporator flows from the portion to be cooled. The refrigerant air may be cooled by the refrigerant liquid, and the regenerator may release the vapor of the refrigerant liquid from the vapor absorbing liquid by the waste heat of the refrigerant air that has exited the compressor.

  In the present invention, the thermally driven cooling unit may be a thermoacoustic cooling unit using a thermoacoustic effect.

In the present invention, in the operation where the set temperature of the cooled part is below a predetermined temperature, only the air cycle refrigeration cooling unit is driven, and in the operation above the predetermined temperature, the air cycle refrigeration cooling unit and the heat driven type are driven. These cooling units may be driven together. The predetermined temperature may be an arbitrary value.
It cannot be used when the set temperature of the part to be cooled is below the solidification temperature of the refrigerant liquid in the heat-driven cooling unit. Therefore, when the set temperature of the cooled part is equal to or lower than a predetermined temperature lower than the freezing point temperature of the refrigerant liquid, the operation of the heat-driven cooling unit is stopped and only the air cycle refrigeration cooling unit is operated. Become.

In the present invention, in the operation where the set temperature of the cooled part is equal to or higher than a predetermined temperature, the air cycle refrigeration cooling unit may be driven for a period of time that can generate the amount of heat necessary for the heat-driven cooling unit. . The predetermined temperature may be an arbitrary value.
In order to operate the air cycle refrigeration cooling unit with high efficiency, it is necessary to rotate the compressor / turbine unit at a high efficiency point, and the number of rotations is determined to be one point. For this reason, the temperature adjustment of the portion to be cooled is handled by intermittently operating the air cycle refrigeration cooling unit. Therefore, in an operation in which the set temperature of the cooled part is equal to or higher than a predetermined temperature, it is desirable to drive the air cycle refrigeration cooling unit for an amount of time during which heat necessary for the heat-driven cooling unit can be generated as an intermittent operation.

In the present invention, a thermoelectric element may be interposed between the compressor and the expansion turbine of the compressor / turbine unit in the air cycle refrigeration cooling unit.
A thermoelectric element is an element utilizing the Bezek effect that generates an electromotive force due to a temperature difference. Since there is a temperature difference of about 150 ° C. between the compressor and the expansion turbine of the compressor / turbine unit, the electromotive force can be taken out from the thermoelectric element using the temperature difference.

In the present invention, outside the compressor / turbine unit in the air cycle refrigeration / cooling unit, the compressor and the expansion turbine are bridged by a heat conducting material, and a thermoelectric element is interposed in the middle of the heat conducting material. Also good. The heat conducting material may be a material having a thermal conductivity similar to that of a steel material, and may be copper, aluminum, or the like.
Also in this configuration example, the electromotive force can be taken out using the temperature difference between the compressor and the expansion turbine.

  In the present invention, the compressor of the compressor / turbine unit in the air cycle refrigeration / cooling unit and the low temperature member outside the compressor / turbine unit are connected by a heat conducting material, and a thermoelectric element is provided in the middle of the heat conducting material. It may be interposed. The low temperature member in this case is, for example, a cover that covers the compressor / turbine unit. Also in this configuration, the electromotive force can be taken out using the temperature difference between the compressor and the low temperature member.

  In this invention, the part to be cooled may be a refrigeration container.

  The hybrid air cycle refrigeration cooling unit of the present invention includes a compressor / turbine unit comprising a combination of a compressor and an expansion turbine, and a heat exchanger, and compresses the refrigerant air flowing in from the cooled portion by the compressor and exchanges the heat. In an air cycle refrigeration cooling unit that performs cooling by a cooler and adiabatic expansion by the expansion turbine to return the cooled refrigerant air into the cooled part, waste of the refrigerant air that has been discharged from the compressor and has reached a high temperature Since a heat-driven cooling unit that uses heat is provided, and a part of the refrigerant air that flows from the cooled part is cooled by this cooling unit and returned to the cooled part, the system efficiency can be improved. .

  An embodiment of the present invention will be described with reference to FIGS. FIG. 1 shows a system diagram of the hybrid air cycle refrigeration cooling unit of this embodiment. This hybrid air cycle refrigeration cooling unit is formed by combining an air cycle refrigeration cooling unit 9 composed of a compressor / turbine unit 5 and two heat exchangers 2 and 3, and a heat driven cooling unit 10. It is an apparatus for directly cooling the air in the cooling unit R as a refrigerant. The part R to be cooled is, for example, a refrigerated container.

  The air cycle refrigeration / cooling unit 9 has a refrigerant path 1 that extends from the in-compartment air inlet Na to the in-compartment outlet Nb that is opened to the cooled portion R, respectively. The compressor / turbine unit 5 includes a combination of a compressor 6 and an expansion turbine 7. A compressor 6 of the compressor / turbine unit 5, a heat exchanger 2 for heat dissipation, a heat exchanger 3 for heat recovery, and an expansion turbine 7 of the compressor / turbine unit 5 are provided in the refrigerant path 1 in this order.

  In the air cycle refrigeration / cooling unit 9, the air (−30 ° C., 0.1 MPa) in the space R to be cooled flows from the outlet into the internal suction port Na of the refrigerant path 1. The air flowing into the internal suction port Na is used for cooling the air in the refrigerant path 1 by the heat recovery heat exchanger 3 and is heated (30 ° C., 0.1 MPa). That is, the heat recovery heat exchanger 3 is between the high-temperature channel 1c into which the air that has exited the heat-dissipating heat exchanger 2 flows and the low-temperature channel 1a into which the low-temperature air that has exited the cooled portion R flows. Heat exchange is performed to cool the air that has exited the heat exchanger 2 for heat dissipation.

  The air that has passed through the low-temperature flow path 1a of the heat recovery heat exchanger 3 is compressed by the compressor 6 of the compressor / turbine unit 5 and is heated by this compression (130 ° C., 0.18 MPa), and is heat-driven cooling. It passes through the unit (50 to 80 ° C.) and is cooled by the heat dissipation heat exchanger 2 (40 ° C.). That is, the heat-dissipating heat exchanger 2 performs heat exchange between the low-temperature flow path 8 into which the outside air supplied by a blower (not shown) flows and 1b, and cools the refrigerant air.

  The air cooled by the heat dissipation heat exchanger 2 is cooled by the heat recovery heat exchanger 3 as described above (−20 ° C., 0.18 MPa), and then insulated by the expansion turbine 7 of the compressor / turbine unit 5. It is cooled by being expanded (−50 ° C., 0.1 MPa) and returned to the cooled part R from the in-compartment outlet Nb. Note that the numerical values of the temperature and the atmospheric pressure shown in the above description are examples that serve as a guide.

  The heat-driven cooling unit 11 cools a part of the refrigerant air flowing in from the cooled portion R by using the waste heat of the refrigerant air that has come out of the compressor 6 in the air cycle refrigeration cooling unit 9 and has reached a high temperature. Then, it is returned to the cooled part R. The heat-driven cooling unit 11 has another refrigerant path 11 that extends from the in-compartment air inlet N1a to the in-compartment outlet N1b of the air that opens in the cooled portion R, respectively.

  FIG. 2 shows a system diagram of an example of the heat-driven cooling unit 10. The heat-driven cooling unit 10 is an adsorption cooling unit including an adsorption / regenerator 30, a condenser 31, and an evaporator 32. The adsorber / regenerator 30 is a container filled with an adsorbent that adsorbs / desorbs the refrigerant liquid vapor, and a plurality of adsorbers are prepared. For example, water or salt water is used as the refrigerant liquid, and zeolite is used as the adsorbent. Each of these adsorption / regenerators 30 is provided with a cooling path 33 for cooling the adsorbent and adsorbing the refrigerant liquid vapor, and drying the adsorbent to dry the refrigerant liquid vapor. 34 is piped. The cooling path 33 is a path through which outside air is supplied as a refrigerant, for example, by a blower (not shown). The drying path 34 is a path through which the refrigerant air having a high temperature of 100 ° C. or more is supplied from the outlet of the compressor 6 and returned to the heat exchanger inlet for heat dissipation. Both the paths 33 and 34 are connected in parallel via a switching valve 35 made of an electromagnetic valve. As a result, when the switching valve 35 is opened and closed, the refrigerant flows through the cooling path 33 to cool the adsorbent, and the high-temperature refrigerant air exiting the compressor 6 flows through the drying path 34 to dry the adsorbent. Can be switched to.

  The condenser 31 is a container for condensing the vapor of the refrigerant liquid desorbed from the adsorbent of the adsorption / regenerator 30, and each adsorption / regenerator is provided by a vapor reflux path 37 in which an on-off valve 36 including an electromagnetic valve is interposed. 30. As a result, the vapor of the refrigerant liquid desorbed from the adsorbent in each adsorption / regenerator 30 is recovered by the condenser 31 through the vapor reflux path 37 by opening the on-off valve 36, where it is condensed and becomes the refrigerant liquid. Returned.

  The evaporator 32 is a container for evaporating the refrigerant liquid taken in from the condenser 31, and the refrigerant path 11 is piped. The evaporator 32 is connected to each adsorption / regenerator 30 by a steam supply path 39 in which an on-off valve 38 made of an electromagnetic valve is interposed. When the on-off valve 38 is opened in a state where the internal pressure of the evaporator 32 and each adsorption / regenerator 30 is reduced to be equal to or lower than the vapor pressure of the refrigerant liquid by evacuation by a vacuum pump (not shown), the refrigerant liquid in the evaporator 32 is removed. The steam flows into each adsorption / regenerator 30 through the vapor supply path 39 and is adsorbed by the adsorbent. The temperature of the refrigerant liquid in the evaporator 32 decreases due to latent heat when evaporating. If the refrigerant liquid is water, it is cooled to 0 ° C, and if it is salt water, it is cooled to about -20 ° C depending on the concentration. Thereby, the refrigerant air from the cooled part R supplied to the steamer 32 via the refrigerant path 11 is cooled and returned to the cooled part R.

  However, since the set temperature of the cooled portion R cannot be used below the solidification temperature of the refrigerant liquid in the heat driven cooling unit 10, the heat driven type is used when the set temperature of the cooled portion R is below a predetermined temperature. The cooling unit 10 is stopped, and only the air cycle refrigeration cooling unit 9 is operated.

  Even if the adsorbent of the adsorber / regenerator 30 adsorbs the refrigerant liquid, it can be repeatedly used by drying it with air or water at about 100 ° C. (here, the refrigerant air discharged from the compressor 6). Therefore, by switching the opening / closing of the switching valve 35 and the opening / closing valves 36 and 38 and switching the process in the adsorption / regenerator 30 to each process of adsorption, drying and cooling, the heat-driven cooling unit 10 can be operated. Cooling in the air conditioning region of the refrigerant air in the cooling unit R can be performed efficiently.

  In this case, the driving power in the heat-driven cooling unit 10 is only switching between opening and closing of the switching valve 35 and the opening / closing valves 36 and 38 made of electromagnetic valves, and evacuation in the previous stage of the adsorption process.

  In order to operate the air cycle refrigeration cooling unit 9 with high efficiency, it is necessary to rotate the compressor / turbine unit 5 at a high efficiency point, and the number of rotations is determined to be one point. For this reason, the temperature adjustment of the cooled portion R is handled by intermittently operating the air cycle refrigeration cooling unit 9. Therefore, in this case, in the operation where the set temperature of the cooled part R is equal to or higher than the predetermined temperature, the air cycle refrigeration cooling unit 9 is driven for a time during which the amount of heat necessary for the heat-driven cooling unit 10 can be generated. . The predetermined temperature may be any temperature that is appropriately determined according to various situations.

  FIG. 3 shows a system diagram of another example of the heat-driven cooling unit 10. The heat-driven cooling unit 10 is an absorption cooling unit that includes an absorber 40, a regenerator 41, a condenser 42, and an evaporator 43. The absorber 40 is a container that contains a vapor absorbing liquid that absorbs the vapor of the refrigerant liquid. For example, water is used as the refrigerant liquid, and an aqueous solution of lithium bromide (LiBr) is used as the vapor absorbing liquid.

  The regenerator 41 is a container that discharges the vapor of the refrigerant liquid from the vapor absorption liquid taken from the absorber 40, and is provided with a vapor heat radiation path 44 that heats the vapor absorption liquid and releases the vapor of the refrigerant liquid. The vapor heat radiation path 44 is a path through which refrigerant air having a high temperature of 100 ° C. or more is supplied from the outlet of the compressor 6 and returned to the heat exchanger inlet for heat radiation.

  The condenser 42 is a container that condenses the vapor of the refrigerant liquid released from the vapor absorbing liquid by the regenerator 41, and is connected to the regenerator 41 by a vapor reflux path 47. Thereby, the vapor | steam of the refrigerant | coolant liquid discharge | released from the vapor | steam absorption liquid in the regenerator 41 is collect | recovered by the condenser 42 via the vapor | steam reflux path 47, and is condensed here and returned to a refrigerant | coolant liquid.

  The evaporator 43 is a container for evaporating the refrigerant liquid taken in from the condenser 42, and the refrigerant path 11 is piped. The evaporator 43 is connected to the absorber 40 by a vapor supply path 49. When the internal pressure of the evaporator 43 and the absorber 40 is reduced by evacuation by a vacuum pump (not shown), the vapor of the refrigerant liquid in the evaporator 43 flows into the absorber 40 through the vapor supply path 49 and is absorbed by the vapor absorbing liquid. Is done. The temperature of the refrigerant liquid in the evaporator 43 decreases due to latent heat when evaporating. Thereby, the refrigerant air from the cooled part R supplied to the steamer 43 via the refrigerant path 11 is cooled and returned to the cooled part R.

  The vapor absorbing liquid in the absorber 40 cannot absorb the vapor when its absorbent concentration is lowered. Therefore, here, the vapor absorbing liquid is circulated between the absorber 40, the regenerator 41, the condenser 42, and the evaporator 43, while the regenerator 41 leaves the compressor 6 supplied via the vapor reflux path 47. The vapor absorbing liquid is heated with high-temperature air to release the vapor. Thereby, the absorbent concentration of the vapor absorbing liquid can be kept within a certain range, and the refrigerant air from the cooled part R can be continuously cooled. Other configurations are the same as those of the adsorption cooling unit.

  FIG. 4 shows a schematic diagram of still another example of the heat-driven cooling unit 10. The heat-driven cooling unit 10 is a thermoacoustic cooling unit using a thermoacoustic effect, which is an energy conversion phenomenon between heat and sound waves, and a stack 51 formed by bundling thin plates or thin tubes is a ring-shaped tube 50. In the middle of the tube 50, another stack 52 is interposed in the other halfway of the tube 50. In this configuration, for example, when a temperature difference is given between both end portions 51 a and 51 b of the stack 51, sound waves are generated from the stack 51. Conversely, when a sound wave is applied to one end of the tube body 50, a temperature difference is generated between both end portions of the stacks 51 and 52.

  Here, a high-temperature flow path 53 that supplies the refrigerant air that has been discharged from the compressor 6 to a high temperature is connected to one end 51a of one stack 51, and the other end 51b of the stack 51 is kept at a constant temperature with cooling water or the like. It keeps in. Further, one end 52b facing the stack one end 51a via the tube 50 of the other stack 52 is kept at a constant temperature with cooling water or the like, and the other end 52a of the stack 52 is connected to the cooled portion R from the cooled portion R. A refrigerant path 11 for circulating and supplying the refrigerant air is piped.

  In the case of this heat-driven cooling unit 10, in one stack 51, one end 51 a heated by high-temperature refrigerant air from the compressor 6 supplied via the high-temperature flow path 53 and the other maintained at a constant temperature. A temperature difference is given to the end 51b. As a result, sound waves are applied to the one end 52b maintained at a constant temperature of the other stack 52 through the tube 50, and a temperature drop occurs at the other end 52a. Heat exchange is performed between the temperature-reduced other end 52a and the refrigerant air flowing through the refrigerant path 11, and the refrigerant air is cooled and returned to the cooled portion R.

  FIG. 5 shows a cross-sectional view of an example of the compressor / turbine unit 5 in the air cycle refrigeration cooling unit 9. The compressor / turbine unit 5 constitutes a compression / expansion turbine system. The compressor / turbine unit 5 includes a compressor 6 and an expansion turbine 7. The compressor impeller 6 a of the compressor 6 and the turbine impeller 7 a of the expansion turbine 7 have a common main shaft 13. The main shaft 13 is supported by a motor-integrated magnetic bearing device.

In FIG. 5, the compressor 6 has a compressor housing 6b facing the compressor impeller 6a via a gap d1, and compresses the air sucked in the axial direction from the suction port 6c in the center with the compressor impeller 6a. As shown by the arrow 6d, it discharges | emits from the exit (not shown) of an outer peripheral part.
The expansion turbine 7 has a turbine housing 7b that opposes the turbine impeller 7a via 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 motor-integrated magnetic bearing device in the compressor / turbine unit 5 includes a main shaft 13 supported by a plurality of bearings 15 and 16 in the radial direction, and either or both of an axial load and a bearing preload applied to the main shaft 13 are magnetic bearings. An axial gap motor 28 is provided which is supported by the electromagnet 17 and the permanent magnet 17A and which rotates the main shaft 13. The compressor / turbine unit 5 includes a sensor 18 that detects a thrust force acting on the main shaft 13, a magnetic bearing controller 19 that controls the supporting force of the electromagnet 17 according to the output of the sensor 18, and the electromagnet 17. A motor controller 29 for controlling the motor 28 independently.

  The electromagnet 17 which is a partial component of the magnetic bearing is composed of two flange-shaped thrust plates 13a made of a ferromagnetic material that is provided perpendicularly and coaxially to the main shaft 13 so as to be aligned in the axial direction at an axial intermediate portion of the main shaft 13. , 13b, one side of the thrust plate 13a located near the compressor 6 facing the compressor 6 is used as a magnet target and is installed in the spindle housing 14 so as to face the one side in a non-contact manner. Further, the permanent magnet 17A, which is another component of the magnetic bearing, has a spindle so that the one surface facing the expansion turbine 7 of the thrust plate 13b located near the expansion turbine 7 is a magnet target and faces this one surface in a non-contact manner. It is installed in the housing 14.

  The motor 28 is a motor unit including a motor rotor 28a provided on the main shaft 13 along with the electromagnet 17 and the permanent magnet 17A, and a motor stator 28b facing the motor rotor 28a in the axial direction. Specifically, the motor rotor 28a constituting one part of the motor unit has a circumferential direction on one side of the main shaft 13 opposite to the side where the electromagnet 17 and the permanent magnet 17A of the thrust plates 13a and 13b face each other. A pair of left and right ones is formed by arranging permanent magnets 28aa arranged at equal pitches. Thus, between the permanent magnets 28aa arranged opposite to each other in the axial direction, the magnetic poles are set to be different from each other.

  The motor stator 28b, which is another part of the motor unit, is disposed without a core so as to face each surface of both the motor rotors 28a in a non-contact manner at a central position in the axial direction between the pair of left and right motor rotors 28a. The plurality of motor coils 28ba and a case 28bb which is an insulating material in which these motor coils 28ba are housed. The case 28bb is fixed to the spindle housing 14. The motor 28 rotates the main shaft 13 by Lorentz force acting between the motor rotor 28a and the motor stator 28b.

  The bearings 15 and 16 that support the main shaft 13 are rolling bearings and have a function of restricting the position in the axial direction. For example, a deep groove ball bearing or an angular ball bearing is 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 rolling 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 main shaft 13 is a stepped shaft having a large-diameter portion 13c at an intermediate portion and small-diameter portions 13d at both ends. The bearings 15 and 16 on both sides have their inner rings 15a and 16a fitted into the small diameter portion 13d in a press-fit state, and one of the width surfaces engages with a stepped surface between the large diameter portion 13c and the small diameter portion 13d. Seals 21 and 22 for sealing a gap with the main shaft 13 are provided at portions of the spindle housing 14 that are closer to the impellers 6a and 7a than the bearings 15 and 16 on both sides.

  The sensor 18 is provided on the stationary side in the vicinity of the bearing 16 on the turbine impeller 7 a side, that is, on the spindle housing 14 side, and also serves as a bearing housing that supports the outer ring 16 b of the bearing 16. The sensor 18 is fitted to the spindle housing 14 so as to be movable in the axial direction. A preload in the axial direction is applied to the sensor 18 by a sensor preload spring 25.

  The preload by the sensor preload spring 25 is to enable the sensor 18 that detects the thrust force by the pressing force to detect any movement of the main shaft 13 in the axial direction. The magnitude is greater than the average thrust force acting on the main shaft 13 in a normal operation state.

  The bearing 15 on the non-arrangement side of the sensor 18 is installed so as to be movable in the axial direction with respect to the spindle housing 14 and is elastically supported by a bearing preload spring 26. In this example, the outer ring 15 b of the bearing 15 is fitted to the inner surface of the spindle housing 14 via the bearing housing 27 so as to be movable in the axial direction, and the bearing preload spring 26 is provided between the bearing housing 27 and the spindle housing 14. Is intervening. The bearing preload spring 26 biases the outer ring 15 b so as to face the step surface of the main shaft 13 with which the width surface of the inner ring 15 a is engaged, and applies a preload to the bearing 15. The bearing preload spring 26 has a smaller spring constant than the sensor preload spring 25.

  As a cooling means for the motor 28, a motor cooling flow path 54 that penetrates an arrangement portion of the motor 28 that is a power portion is provided in the spindle housing 14. This motor cooling flow path 54 is interposed in the refrigerant flow path 1 of the air cycle refrigeration cooling unit 9 of FIG. Specifically, in FIG. 1, the air that has passed through the heat dissipation heat exchanger 2 from the compressor 6 flows through the motor cooling flow path 54, whereby the motor rotor 28 a of the motor 28 is cooled.

  A thermoelectric element 55 is interposed between the spindle housing 14 between the compressor 6 side (compressor housing 6b) and the expansion turbine 7 side (turbine housing 7b). The thermoelectric element 55 is an element using the Bezek effect that generates an electromotive force due to a temperature difference. Since there is a temperature difference of about 150 ° C. between the high temperature side compressor 6 side of the spindle housing 14 and the low temperature side expansion turbine 7 side, an electromotive force is taken out from the thermoelectric element 55 using this temperature difference. be able to.

  FIG. 6 is a sectional view of another example of the compressor / turbine unit 5. In the example of FIG. 5, the compressor / turbine unit 5 is formed by bridging the compressor 6 side and the expansion turbine 7 side with a heat conducting material 56 outside the spindle housing 14, and a midway portion of the heat conducting material 56. The thermoelectric element 55 is interposed therebetween. The heat conducting material 56 may be a material having a thermal conductivity equivalent to that of a steel material, and may be copper, aluminum, a steel material, or the like. Other configurations are the same as those in the example of FIG. Also in this configuration example, the electromotive force can be taken out using the temperature difference in the spindle housing 14.

  FIG. 7 is a sectional view of still another example of the compressor / turbine unit 5. In the example of FIG. 5, the compressor / turbine unit 5 is formed by connecting the outlet portion of the compressor 6 on the high temperature side of the spindle housing 14 and the low temperature member 57 outside the compressor / turbine unit 5 with a heat conducting material 56. The thermoelectric element 55 is interposed in the middle of the heat conducting material 56. The low temperature member 57 in this case is, for example, a cover that covers the compressor / turbine unit 5. Other configurations are the same as those in the example of FIG. Also in this configuration, the electromotive force can be taken out using the temperature difference between the compressor 5 and the external low-temperature member 57.

It is a systematic diagram of the hybrid air cycle refrigeration cooling unit concerning one embodiment of this invention. It is a systematic diagram of an example of the heat drive type cooling unit in the hybrid air cycle refrigeration cooling unit. It is a systematic diagram of the other example of the cooling unit of the same heat drive type. It is the schematic of the further another example of the cooling unit of the same heat drive type. It is sectional drawing of an example of the compressor turbine unit in the air cycle refrigeration cooling unit of a hybrid air cycle refrigeration cooling unit. It is sectional drawing of the other example of the compressor-turbine unit. It is sectional drawing of the further another example of the compressor-turbine unit.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1,11 ... Refrigerant path 2 ... Heat exchanger 3 for heat dissipation ... Heat exchanger 5 for heat recovery ... Compressor turbine unit 6 ... Compressor 6b ... Compressor housing 7 ... Expansion turbine 7b ... Turbine housing 9 ... Air cycle refrigeration cooling unit 10 ... Heat-driven cooling unit 14 ... Spindle housing 30 ... Adsorption / regenerator 31 ... Condenser 32 ... Evaporator 40 ... Absorber 41 ... Regenerator 42 ... Condenser 43 ... Evaporator 50 ... Tube 51, 52 ... Stack 51a, 51b, 52a, 52b ... Stack end 55 ... Thermoelectric element 56 ... Thermally conductive material 57 ... Low temperature member

Claims (10)

A compressor / turbine unit comprising a combination of a compressor and an expansion turbine and a heat exchanger are provided, and the refrigerant air flowing in from the cooled part is compressed by the compressor, cooled by the heat exchanger, and adiabatic expansion by the expansion turbine. In the air cycle refrigeration / cooling unit configured to return the refrigerant air cooled thereby into the cooled portion,
A heat-driven cooling unit that uses the waste heat of the refrigerant air that has been discharged from the compressor and that has become hot is provided, and this cooling unit cools a part of the refrigerant air that flows from the cooled part to enter the cooled part. A hybrid air cycle refrigeration cooling unit characterized by being returned.   2. The heat-driven cooling unit according to claim 1, wherein the adsorption / regenerator filled with an adsorbent that adsorbs / desorbs the vapor of the refrigerant liquid, a condenser that condenses the vapor desorbed from the adsorbent, An adsorption type cooling unit that evaporates the condensed refrigerant liquid and supplies it to the adsorption / regenerator, wherein the evaporator cools the refrigerant air flowing in from the cooled portion with the refrigerant liquid, and A hybrid air cycle refrigeration cooling unit in which the adsorbent is dried by the waste heat of the refrigerant air that has exited the compressor to desorb the vapor of the refrigerant liquid from the adsorbent in the regenerator.   2. The heat-driven cooling unit according to claim 1, wherein the heat-driven cooling unit accommodates a vapor absorbing liquid and absorbs the vapor of the refrigerant liquid, a regenerator that releases the vapor of the refrigerant liquid from the vapor absorbing liquid, and the vapor absorbing liquid. An absorption cooling unit comprising a condenser for condensing the vapor of the refrigerant liquid discharged from the refrigerant and an evaporator for evaporating the condensed refrigerant liquid and supplying the condensed refrigerant liquid to the absorber. In the evaporator, the refrigerant flows from the cooling unit. A hybrid air cycle refrigeration cooling unit in which the refrigerant air is cooled by a refrigerant liquid, and in the regenerator, the vapor of the refrigerant liquid is released from the vapor absorbing liquid by the waste heat of the refrigerant air exiting the compressor.   2. The hybrid air cycle refrigeration cooling unit according to claim 1, wherein the heat-driven cooling unit is a thermoacoustic cooling unit using a thermoacoustic effect.   5. The operation according to claim 1, wherein only the air cycle refrigeration unit is driven when the set temperature of the portion to be cooled is a predetermined temperature or less, and the air is operated when the set temperature is a predetermined temperature or more. A hybrid air cycle refrigeration cooling unit that drives both the cycle refrigeration cooling unit and the heat-driven cooling unit.   6. The operation according to claim 5, wherein the air cycle refrigeration cooling unit is driven for a period of time capable of generating the amount of heat necessary for the heat-driven cooling unit when the set temperature of the cooled part is at a predetermined temperature or higher. Hybrid air cycle refrigeration unit.   The hybrid air cycle refrigeration cooling unit according to any one of claims 1 to 6, wherein a thermoelectric element is interposed between a compressor and an expansion turbine of the compressor / turbine unit in the air cycle refrigeration cooling unit.   7. The heat conducting material according to claim 1, wherein the compressor and the expansion turbine are bridged by a heat conducting material outside the compressor / turbine unit in the air cycle refrigeration cooling unit. A hybrid air cycle refrigeration / cooling unit with a thermoelectric element in the middle.   7. The compressor of the compressor / turbine unit in the air cycle refrigeration / cooling unit and a low-temperature member outside the compressor / turbine unit are connected by a heat conducting material according to claim 1, A hybrid air cycle refrigeration cooling unit with a thermoelectric element in the middle of the good conducting material.   The hybrid air cycle refrigeration cooling unit according to any one of claims 1 to 9, wherein the portion to be cooled is a refrigeration container.

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