JP2009276052A - Ejector type refrigeration cycle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To stably operate an ejector type refrigeration cycle even with a change in the flow rate of driving flow that passes through a nozzle of an ejector. <P>SOLUTION: In a cooling operation mode, a refrigerant flowing out of an outdoor heat exchanger 41 is reduced in pressure by the ejector 13, and a second compression mechanism 21a is driven to suck and compress a refrigerant flowing out of a utilization side heat exchanger 51 and to discharge the refrigerant to the refrigerant suction port 13b side of the ejector 13. In a heating operation mode, the refrigeration cycle is switched to a cycle of circulating a refrigerant in the order of a first compression mechanism 11a → the utilization side heat exchanger 51 → a fixed throttle 18 → an outdoor heat exchanger 41 → the first compression mechanism 11a. Consequently, even if the driving flow of the ejector 13 is lowered in the cooling operation mode, the suction capacity of the ejector 13 is assisted by the second compression mechanism 21a, and a refrigeration cycle can be constituted without using the ejector 13 in the heating operation mode. The cycle can thereby be stably operated in any operation mode. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an ejector-type refrigeration cycle having an ejector.

  2. Description of the Related Art Conventionally, an ejector refrigeration cycle having an ejector that functions as a refrigerant decompression unit and a refrigerant circulation unit is known. For example, Patent Documents 1 to 3 disclose an ejector-type refrigeration cycle in which a compressor discharge refrigerant dissipates heat by exchanging heat with outdoor air using a radiator and decompresses the dissipated high-pressure refrigerant at a nozzle portion of the ejector. ing.

  For example, in the ejector-type refrigeration cycle of Patent Document 1, a gas-liquid separator that separates the gas-liquid of the low-pressure refrigerant is disposed downstream of the diffuser portion of the ejector, and the gas-phase refrigerant outlet of the gas-liquid separator is connected to the compressor inlet side. And the liquid-phase refrigerant outlet is connected to the inlet of the suction-side evaporator, and the outlet of the suction-side evaporator is connected to the refrigerant suction port of the ejector.

  Further, in the ejector refrigeration cycle of Patent Document 2, a branching portion for branching the flow of the refrigerant flowing out from the radiator is provided on the upstream side of the nozzle portion of the ejector, and one of the refrigerants branched at the branching portion is ejected from the nozzle of the ejector. The other refrigerant is caused to flow into the refrigerant suction port side of the ejector.

  An outlet-side evaporator that evaporates the refrigerant that has flowed out of the diffuser portion is disposed downstream of the diffuser portion of the ejector, and a fixed throttle that decompresses and expands the refrigerant between the branch portion and the refrigerant suction port of the ejector. A suction-side evaporator is arranged. As a result, the refrigerating capacity can be exhibited in both evaporators.

  Further, in the ejector refrigeration cycle of Patent Document 3, a branching part for branching the flow of the refrigerant flowing out from the diffuser part is provided on the downstream side of the diffuser part of the ejector, and one of the refrigerants branched at the branching part is supplied to the outflow evaporator. The other refrigerant is caused to flow into the refrigerant suction port side of the ejector through the suction side evaporator. As a result, the refrigerating capacity can be exhibited in both evaporators.

  In an ejector applied to this type of ejector-type refrigeration cycle, high-pressure refrigerant is decompressed and expanded at the nozzle portion of the ejector, and the refrigerant on the downstream side of the evaporator is sucked from the refrigerant suction port by the pressure drop of the injected refrigerant. Thus, the loss of kinetic energy at the time of decompression expansion in the nozzle portion is recovered.

  Then, the recovered kinetic energy (hereinafter referred to as “recovered energy”) is converted into pressure energy by the diffuser portion of the ejector, and the pressure of the compressor suction refrigerant is increased. Thereby, the drive power of a compressor is reduced and the coefficient of performance (COP) of an ejector type refrigeration cycle is improved.

  Patent Document 4 is configured to be able to switch between a cooling operation mode refrigerant flow path for cooling indoor blown air that is a heat exchange target fluid and a heating operation mode refrigerant flow path for heating indoor blowing air. An ejector refrigeration cycle is disclosed.

Japanese Patent No. 3322263 Japanese Patent No. 3931899 JP 2008-107055 A JP 2002-327967 A

  However, in this type of ejector-type refrigeration cycle, the suction capacity of the ejector decreases as the flow rate of refrigerant (hereinafter referred to as drive flow) passing through the nozzle portion decreases, so the amount of recovered energy also decreases. End up. For this reason, the above-mentioned COP improvement effect will reduce with the flow volume fall of a drive flow.

  For example, in the ejector refrigeration cycle of Patent Document 1, when the pressure of the high-pressure refrigerant decreases as the outside air temperature decreases, the pressure difference between the high-pressure refrigerant and the low-pressure refrigerant decreases, and the flow rate of the ejector drive flow decreases. End up.

  When such a decrease in the flow rate of the drive flow occurs, not only the suction capacity of the ejector is reduced and the amount of recovered energy is reduced, but also the liquid-phase refrigerant is hardly supplied from the gas-liquid separator to the evaporator, and the cycle is The refrigeration capacity that can be exerted also decreases. As a result, the COP is significantly reduced as the driving flow rate decreases.

  Furthermore, if the suction capability of the ejector is reduced and refrigerant is no longer supplied to the evaporator, the low-pressure refrigerant cannot exhibit the endothermic effect in the evaporator, causing a problem that the cycle breaks down.

  This will be described in detail with reference to FIG. FIG. 50 is a Mollier diagram showing the state of the refrigerant in the ejector refrigeration cycle of Patent Document 1 (see FIG. 2 of Patent Document 1). Note that the solid line in FIG. 50 indicates the state of the refrigerant during normal operation, and the broken line indicates the state of the refrigerant when the above-described cycle failure occurs.

As is clear from FIG. 50, when the pressure difference between the high-pressure refrigerant and the low-pressure refrigerant decreases due to a decrease in the outside air temperature or the like (the white arrow X _{50 in} FIG. ₅₀ ), the suction capability of the ejector decreases. As a result, when the refrigerant is not supplied to the evaporator, the low-pressure refrigerant cannot exhibit the endothermic action in the evaporator (the white arrow Y _{50 in} FIG. ₅₀ ).

  For this reason, as shown by the broken line in FIG. 50, the amount of heat that can be radiated from the refrigerant by the radiator becomes equivalent to the compression work of the compressor. As a result, the amount of heat cannot be substantially transferred from the low pressure side to the high pressure side via the refrigerant, and the cycle fails.

  On the other hand, in the ejector type refrigeration cycle of Patent Document 2, the refrigerant flow path from the branch portion to the refrigerant suction port via the fixed throttle and the suction side evaporator is connected in parallel to the nozzle portion of the ejector. Therefore, the refrigerant that has flowed into the suction-side evaporator can be led out to the refrigerant suction port by using the refrigerant suction and discharge capabilities of the compressor.

  Therefore, even if the flow rate of the drive flow is reduced due to the reduction in the pressure difference between the high-pressure refrigerant and the low-pressure refrigerant, and the amount of energy recovered by the ejector is reduced, the refrigerant is transferred to the suction side evaporator and the outflow side evaporator by the action of the compressor Can be supplied.

  Thereby, cycle failure like the ejector type refrigerating cycle of patent documents 1 can be avoided. However, it cannot be avoided that the amount of pressure increase in the diffuser portion and the COP decrease due to the decrease in the flow rate of the driving flow.

  Further, in the ejector refrigeration cycle of Patent Document 3, the refrigerant can be caused to flow in an annular manner in the order of compressor → radiator → ejector → outflow side evaporator → compressor. Therefore, even if the flow rate of the driving flow is reduced due to the reduction in the pressure difference between the high-pressure refrigerant and the low-pressure refrigerant, and the suction capability of the ejector is reduced, the refrigerant is supplied to the outflow evaporator by the refrigerant suction and discharge action of the compressor. be able to.

  Thereby, cycle failure like the ejector type refrigerating cycle of patent documents 1 can be avoided. However, it is not possible to avoid a decrease in COP due to a decrease in the amount of pressure increase in the diffuser section and a decrease in COP due to the inability to supply refrigerant to the suction side evaporator as the flow rate of the driving flow decreases. .

  That is, in the ejector type refrigeration cycle using the ejector as the refrigerant pressure reducing means, there is a problem that when the flow rate fluctuation of the driving flow occurs, the cycle cannot be stably operated while exhibiting a high COP. Moreover, in the ejector-type refrigeration cycle configured to be able to switch between the cooling operation mode and the heating operation mode as in Patent Document 4, the same problem occurs when at least the ejector is switched to the refrigerant flow path used as the refrigerant decompression means. Arise.

  The present invention has been made in view of the above points, and an object of the present invention is to stably operate an ejector refrigeration cycle even when the flow rate fluctuation of the drive flow of the ejector occurs.

In order to achieve the above object, in the first aspect of the present invention, the first and second compression mechanisms (11a, 21a) for compressing and discharging the refrigerant and heat exchange between the refrigerant and the outside air are performed. An outdoor heat exchanger (41) to be used, a use side heat exchanger (51) for exchanging heat between the refrigerant and the heat exchange target fluid, and a high-speed jet refrigerant injected from the nozzle section (13a) for decompressing and expanding the refrigerant An ejector (13) for sucking the refrigerant from the refrigerant suction port (13b) by the flow and increasing the pressure of the mixed refrigerant of the injected refrigerant and the suction refrigerant sucked from the refrigerant suction port (13b) at the diffuser portion (13d); Refrigerant depressurization means (18) for depressurizing and expanding the refrigerant, refrigerant flow path for cooling operation mode for cooling the heat exchange target fluid, and refrigerant flow path switching for switching the refrigerant flow path for heating operation mode for heating the heat exchange target fluid means( 1,32,33) and equipped with a,
The refrigerant flow switching means (31 to 33) is configured to supply the refrigerant discharged from the first compression mechanism (11a) to the outdoor heat exchanger (41) and the use side heat exchanger in one of the cooling operation mode and the heating operation mode. (51), heat is radiated by one of the heat exchangers, and the refrigerant radiated by one of the heat exchangers is caused to flow into the nozzle portion (13a), and the outdoor heat exchanger (41) and the use side heat exchanger ( 51), the refrigerant evaporated in the other heat exchanger is sucked into the second compression mechanism (21a) and switched to the refrigerant flow path for discharge to the refrigerant suction port (13b), and the cooling operation mode and the heating operation mode are switched. During the other operation mode, the refrigerant discharged from one of the first and second compression mechanisms (11a, 21a) is radiated by the other heat exchanger, and the other heat exchanger Refrigerant that has dissipated heat It causes to flow into pressure means (18), and wherein the refrigerant cycle for switching a refrigerant flow path for inhaling refrigerant evaporated in one of the heat exchangers to one compression mechanism.

  According to this, during one operation mode, the refrigerant flowing out of one of the outdoor heat exchanger (41) and the use side heat exchanger (51) functioning as a radiator is discharged from the nozzle of the ejector (13). The refrigerant sucked out from the other heat exchanger functioning as an evaporator among the outdoor heat exchanger (41) and the use side heat exchanger (51) is decompressed by the section (13a), and the refrigerant suction port of the ejector (13) An ejector type refrigeration cycle is formed from (13b).

  In one operation mode in which the ejector refrigeration cycle is configured, the second compression mechanism (21a) is moved from the other heat exchanger functioning as an evaporator to the refrigerant suction port (13b) side of the ejector (13). Since the refrigerant is discharged, it is possible to assist the suction capability of the ejector (13) even under operating conditions in which the suction capability of the ejector (13) decreases as the drive flow rate of the ejector (13) decreases. it can.

  Therefore, in one operation mode in which the ejector-type refrigeration cycle is configured, the cycle is stably operated even under an operation condition in which the flow rate fluctuation of the drive flow occurs and the suction capacity of the ejector (13) decreases. be able to.

  Moreover, since the pressure of the refrigerant can be increased by the pressure increasing action of the two first and second compression mechanisms (11a, 21a) and the diffuser portion (13d) of the ejector (13), the pressure of the refrigerant is increased by one compression mechanism. Thus, the COP can be improved by reducing the driving power of the first and second compression mechanisms (11a, 21a).

  That is, not only can the compressor drive power of the first compression mechanism (11a) be reduced by increasing the suction pressure of the first compression mechanism (11a) by the pressure increasing action of the diffuser portion (13d), Since the pressure difference between the suction pressure and the discharge pressure of each of the first and second compression mechanisms (11a, 21a) can be reduced, the compression efficiency of the first and second compression mechanisms (11a, 21a) is improved and COP is reduced. It can be improved.

  Thus, the ability to stably operate the ejector refrigeration cycle while exhibiting a high COP means that the pressure difference between the high-pressure refrigerant and the low-pressure refrigerant increases in one operation mode, for example, one operation mode A cold storage room that sometimes reduces the internal temperature to a very low temperature (for example, about −30 ° C. to −10), or a cold storage room that is used in an environment where the outside air as an endothermic source is at a very low temperature in one operation mode. It is extremely effective when applied to the above.

  In the other operation mode, the refrigerant discharged from one of the first and second compression mechanisms (11a, 21a) is used as the other heat exchanger functioning as a radiator → refrigerant decompression means ( 18) → One heat exchanger functioning as an evaporator → A refrigeration cycle that circulates to one compression mechanism can be configured.

  In this cycle, since the ejector (13) is not used as the refrigerant pressure reducing means, the operation of the cycle does not become unstable due to a decrease in the suction capability of the ejector (13). Accordingly, the cycle can be stably operated even in the other operation mode.

According to a second aspect of the present invention, in the ejector refrigeration cycle according to the first aspect, the gas-liquid refrigerant is separated, and the separated gas-phase refrigerant is allowed to flow out to the suction port side of the first compression mechanism (11a). A gas-liquid separator (14), and a separation refrigerant decompression means (15) for decompressing and expanding the liquid-phase refrigerant separated by the gas-liquid separator (14),
In one operation mode, the refrigerant flow switching means (31 to 33) causes the refrigerant flowing out of the diffuser part (13d) to be sucked into the first compression mechanism (11a) via the gas-liquid separator (14) and separated refrigerant. The refrigerant is characterized in that it is switched to a refrigerant flow path for allowing the refrigerant decompressed and expanded by the decompression means (15) to flow into the other heat exchanger.

  Thus, specifically, in one operation mode, the liquid-phase refrigerant separated by the gas-liquid separator (14) is decompressed and expanded by the separated refrigerant decompression means (15), and the decompressed and expanded refrigerant is An ejector refrigeration cycle that evaporates in a heat exchanger can be configured. Further, in any operation mode, the gas-phase refrigerant separated by the gas-liquid separator (14) is sucked into the first compression mechanism (11a), so that the problem of liquid compression of the first compression mechanism (11a) is eliminated. Can be avoided.

  Further, in the ejector refrigeration cycle according to claim 2, as in the invention according to claim 3, one compression mechanism is the first compression mechanism (11a), and the refrigerant flow switching means (31 to 33). ) Causes the refrigerant decompressed and expanded by the refrigerant decompression means (18) to flow into one of the heat exchangers in the other operation mode, and the refrigerant flowing out of the one of the heat exchangers is converted into a gas-liquid separator (14). The refrigerant flow path may be switched to be sucked into the first compression mechanism (11a).

  Further, as in the invention according to claim 4, one compression mechanism is the second compression mechanism (21a), and the refrigerant flow switching means (31 to 33) is the refrigerant decompression means in the other operation mode. The refrigerant expanded under reduced pressure in (18) flows into one heat exchanger, and the refrigerant flowing out from one heat exchanger bypasses the gas-liquid separator (14) to the first compression mechanism (11a). You may make it switch to the refrigerant | coolant flow path made to inhale.

  Thus, specifically, in the other operation mode, a cycle can be configured in which the refrigerant decompressed and expanded by the refrigerant decompression means (18) is evaporated by one heat exchanger functioning as an evaporator.

According to a fifth aspect of the present invention, in the ejector refrigeration cycle according to the first aspect, the flow of the refrigerant flowing into the nozzle portion (13a) is branched, and one of the branched refrigerants is moved to the nozzle portion (13a) side. An upstream branch (22) that flows out into
In one operation mode, the refrigerant flow switching means (31, 32) causes the other refrigerant branched at the upstream branching section (22) to flow into the refrigerant decompression means (18), and the refrigerant decompression means (18). The refrigerant depressurized in step S3 is caused to flow into the other heat exchanger, and further, the refrigerant flowed out of the diffuser portion (13d) is switched to a refrigerant flow path for sucking into the first compression mechanism (11a). It is characterized in that the refrigerant decompressed and expanded by the refrigerant decompression means (18) is switched to a refrigerant flow path for flowing into one heat exchanger via the upstream branching section (22).

  Thus, specifically, in one operation mode, the other refrigerant branched in the upstream branching section (22) is decompressed and expanded by the refrigerant decompression means (18), and the decompressed and expanded refrigerant is heated to the other heat. An ejector refrigeration cycle that evaporates in an exchanger can be configured. Moreover, the refrigeration cycle which does not use an ejector (13) as a refrigerant | coolant decompression means can be comprised at the time of the other operation mode.

  According to a sixth aspect of the present invention, in the ejector refrigeration cycle according to the fifth aspect, in one operation mode, the refrigerant flowing out of the diffuser portion (13d) and sucked into the first compression mechanism (11a) is evaporated. An outflow side heat exchanger (52) is provided.

  According to this, not only the heat exchanger functioning as an evaporator among the outdoor heat exchanger (41) and the use side heat exchanger (51) but also the outflow side heat exchanger (52) in one operation mode. The refrigerant can exhibit an endothermic effect. Therefore, in one operation mode, the outflow side heat exchanger (52) can be used for cooling another heat exchange target fluid.

  Further, in one operation mode, in the heat exchanger functioning as an evaporator, the refrigerant evaporating pressure is equivalent to the suction pressure on the second compression mechanism (21a), and in the outflow side heat exchanger (52), the diffuser portion (13d ), The refrigerant evaporating pressure after being increased in pressure can be set to different temperatures for the heat exchanger functioning as an evaporator and the refrigerant evaporating temperature of the outflow side heat exchanger (52).

  Further, as in the invention described in claim 7, in the ejector refrigeration cycle according to claim 6, one compression mechanism is the first compression mechanism (11a), and the refrigerant flow switching means (31, 32). ) Is switched to the refrigerant flow path for evaporating the refrigerant flowing out of the diffuser section (14d) in the outflow side heat exchanger (52) in one operation mode, and is switched to the outflow side heat exchanger (52) in the other operation mode. Then, the refrigerant flow path may be switched to evaporate the refrigerant flowing out from the one heat exchanger.

  As in the invention described in claim 8, in the ejector refrigeration cycle described in claim 6, one compression mechanism is the first compression mechanism (11a), and the refrigerant flow switching means (31, 32). ) Is switched to the refrigerant flow path for evaporating the refrigerant flowing out of the diffuser section (14d) in the outflow side heat exchanger (52) in one operation mode, and is switched to the outflow side heat exchanger (52) in the other operation mode. The first compression mechanism (11a) may be switched to a refrigerant flow path that radiates the discharged refrigerant.

  As in the invention described in claim 9, in the ejector refrigeration cycle according to claim 6, one compression mechanism is the second compression mechanism (21a), and the refrigerant flow switching means (31, 32). ) Is switched to the refrigerant flow path for evaporating the refrigerant flowing out of the diffuser section (14d) in the outflow side heat exchanger (52) in one operation mode, and is switched to the outflow side heat exchanger (52) in the other operation mode. Then, it may be switched to a refrigerant flow path for evaporating the refrigerant flowing out from one of the heat exchangers.

  In the invention according to claim 10, in the ejector refrigeration cycle according to any one of claims 5 to 9, the ejector refrigeration cycle is disposed between the upstream branching portion (22) and the refrigerant pressure reducing means (18), In one operation mode, the other refrigerant branched at the upstream branching section (22) is radiated, and in the other operation mode, auxiliary heat exchange is performed to evaporate the refrigerant expanded under reduced pressure by the refrigerant decompression means (18). It is provided with a vessel (53).

  According to this, the auxiliary heat exchanger (53) can be used for heating another heat exchange target fluid in one operation mode, and is used for cooling another heat exchange target fluid in the other operation mode. be able to.

  Further, during one operation mode in which the ejector refrigeration cycle is configured, the auxiliary heat exchanger (53) dissipates the other refrigerant branched at the upstream branching portion (22), so that the upstream branching portion ( The enthalpy of the refrigerant flowing into the nozzle portion (13a) of the ejector (13) is not unnecessarily lowered. Thereby, COP can be improved by increasing the amount of recovered energy in the nozzle part (13a).

  According to an eleventh aspect of the present invention, in the ejector refrigeration cycle according to any one of the fifth to tenth aspects, in one operation mode, the other refrigerant branched at the upstream branch portion (22) The second compression mechanism (21a) includes an internal heat exchanger (35) for exchanging heat with the sucked refrigerant.

  According to this, during one operation mode, the enthalpy difference (refrigeration capacity) between the enthalpy of the other heat exchanger inlet side refrigerant that functions as an evaporator and the enthalpy of the outlet side refrigerant is expanded, and the COP is further increased. It can be improved.

  According to a twelfth aspect of the present invention, in the ejector refrigeration cycle according to any one of the fifth to tenth aspects, in one operation mode, the refrigerant in the decompression / expansion process in the refrigerant decompression means (18), and the second The compression mechanism (21a) includes an internal heat exchanger (36) for exchanging heat with the suction refrigerant.

  According to this, during one operation mode, the enthalpy difference (refrigeration capacity) between the enthalpy of the other heat exchanger inlet side refrigerant that functions as an evaporator and the enthalpy of the outlet side refrigerant is expanded, and the COP is further increased. It can be improved.

In the invention according to claim 13, in the ejector refrigeration cycle according to claim 1, the downstream branching portion (23) for branching the flow of the refrigerant flowing out from the diffuser portion (13d), and at one operation mode, The outflow side heat exchanger (52) that evaporates one refrigerant branched in the downstream branch section (23), and the other refrigerant branched in the downstream branch section (23) in one operation mode. Low pressure side decompression means (19b) for decompression expansion,
The refrigerant flow switching means (31 to 33) causes the refrigerant flowing out from the outflow side heat exchanger (52) to be sucked into the first compression mechanism (11a) in the one operation mode, and is caused to be in the low pressure side decompression means (19b). The refrigerant that has been decompressed and expanded is switched to the refrigerant flow path that allows the refrigerant to flow into the other heat exchanger, and the refrigerant that has been decompressed and expanded by the refrigerant depressurizing means (18) flows into the one heat exchanger in the other operation mode. It is characterized by switching to a flow path.

  According to this, specifically, in one operation mode, one refrigerant branched in the downstream branch section (23) is evaporated in the outflow side heat exchanger (52), and the downstream branch section ( An ejector refrigeration cycle in which the other refrigerant branched in 23) is decompressed and expanded by the low-pressure side decompression means (19b) and evaporated by the other heat exchanger can be configured. Moreover, the refrigeration cycle which does not use an ejector (13) as a refrigerant | coolant decompression means can be comprised at the time of the other operation mode.

  Further, as in the invention described in claim 14, in the ejector refrigeration cycle according to claim 13, one compression mechanism is the first compression mechanism (11a), and the refrigerant flow switching means (31-33). ) Is switched to the refrigerant flow path for evaporating the refrigerant flowing out of the diffuser section (14d) in the outflow side heat exchanger (52) in one operation mode, and is switched to the outflow side heat exchanger (52) in the other operation mode. Then, the refrigerant may be switched to a refrigerant flow path that radiates the refrigerant discharged from the first compression mechanism (11a).

  As in the invention described in claim 15, in the ejector refrigeration cycle described in claim 13, one compression mechanism is the second compression mechanism (21a), and the refrigerant flow switching means (31-33). ) Is switched to a refrigerant flow path for evaporating the refrigerant flowing out of the diffuser part (14d) in the outflow side heat exchanger (52) in one operation mode, and the refrigerant flows out from one heat exchanger in the other operation mode. It switches to the refrigerant | coolant flow path which evaporates.

In the invention described in claim 16, the first and second compression mechanisms (11a, 21a) for compressing and discharging the refrigerant, and the discharge side branching portion for branching the flow of the refrigerant discharged from the first compression mechanism (11a) (24), a heat-dissipating heat exchanger (54) that dissipates one of the refrigerants branched at the discharge-side branching part (24), and a nozzle that decompresses and expands the refrigerant flowing out of the heat-dissipating heat exchanger (54) The refrigerant is sucked from the refrigerant suction port (13b) by the flow of the high-speed jet refrigerant jetted from the section (13a), and the mixed refrigerant of the jetted refrigerant and the sucked refrigerant sucked from the refrigerant suction port (13b) is diffuser part An ejector (13) whose pressure is increased in (13d), an outdoor heat exchanger (41) for exchanging heat between the refrigerant and the outside air, and a use-side heat exchanger (51) for exchanging heat between the refrigerant and the heat exchange target fluid. , Refrigerant decompression to expand the refrigerant under reduced pressure A refrigerant channel switching means (31, 32) for switching the stage (18), a refrigerant channel in a cooling operation mode for cooling the heat exchange target fluid, and a refrigerant channel in a heating operation mode for heating the heat exchange target fluid; With
The refrigerant flow switching means (31, 32) is configured so that the other refrigerant branched in the discharge side branch section (24) is transferred to the outdoor heat exchanger (41) in one of the cooling operation mode and the heating operation mode. In addition, heat is radiated by one of the heat exchangers (51) of the use side heat exchanger (51), and the refrigerant radiated by one of the heat exchangers is caused to flow into the refrigerant decompression means (18) and the outdoor heat exchanger (41) And the refrigerant | coolant which evaporated by the other heat exchanger among the use side heat exchangers (51) is suck | inhaled to a 2nd compression mechanism (21a), and it switches to the refrigerant | coolant flow path discharged to a refrigerant | coolant suction port (13b) side, and is cooled. During the other operation mode of the operation mode and the heating operation mode, the refrigerant discharged from one of the first and second compression mechanisms (11a, 21a) is radiated by the other heat exchanger, Release in the other heat exchanger It causes the refrigerant to flow into the refrigerant pressure reducing means (18), and wherein the refrigerant cycle for switching a refrigerant flow path for inhaling refrigerant evaporated in one of the heat exchangers to one compression mechanism.

  According to this, specifically, in one operation mode, one refrigerant branched in the discharge-side branching section (24) is discharged to the nozzle of the ejector (13) through the heat dissipation heat exchanger (54). And the other refrigerant branched at the discharge side branching section (24) is supplied to the other heat exchanger via the one heat exchanger and the refrigerant pressure reducing means (18). Thus, an ejector refrigeration cycle that evaporates can be configured.

  In one operation mode in which the ejector refrigeration cycle is configured, the second compression mechanism (21a) is ejected from the other heat exchanger functioning as an evaporator (ejector) in the same manner as in the first aspect of the invention. Since the refrigerant is discharged to the refrigerant suction port (13b) side of 13), even if the operating conditions are such that the flow rate fluctuation of the drive flow of the ejector (13) occurs and the suction capacity of the ejector (13) is reduced, the cycle Can be operated stably.

  Furthermore, since the heat exchange capability (heat radiation performance) of the heat exchanger for heat radiation (54) and one heat exchanger can be changed independently in one operation mode, for example, heat exchange of one heat exchanger. The capacity (heat radiation performance) and the heat exchange capacity (heat absorption performance) of the other heat exchanger can be easily adapted. Therefore, it is easier to stabilize the operation of the cycle.

  Furthermore, by adopting a heat dissipation heat exchanger (54) whose heat exchange capacity is lower than that of one heat exchanger, the enthalpy of the refrigerant flowing into the nozzle portion (13a) of the ejector (13) is reduced. It is possible to avoid a necessary decrease. Thereby, the amount of recovered energy in the nozzle part (13a) can be increased, and COP can be improved.

  Moreover, at the time of the other operation mode, the refrigerating cycle which does not use the ejector (13) similar to the invention of Claim 1 as a refrigerant | coolant decompression means can be comprised. Accordingly, the cycle can be stably operated even in the other operation mode.

  In the invention according to claim 17, in the ejector type refrigeration cycle according to claim 16, in one operation mode, the refrigerant flowing out of the diffuser portion (13d) and sucked into the first compression mechanism (11a) is evaporated. An outflow side heat exchanger (52) is provided.

  According to this, not only the heat exchanger functioning as an evaporator among the outdoor heat exchanger (41) and the use side heat exchanger (51) but also the outflow side heat exchanger (52) in one operation mode. The refrigerant can exhibit an endothermic effect.

  As in the invention described in claim 18, in the ejector refrigeration cycle described in claim 17, one compression mechanism is the first compression mechanism (11a), and the refrigerant flow switching means (31, 32). ) Is switched to the refrigerant flow path for evaporating the refrigerant flowing out of the diffuser section (14d) in the outflow side heat exchanger (52) in one operation mode, and is switched to the outflow side heat exchanger (52) in the other operation mode. Then, it may be switched to a refrigerant flow path for evaporating the refrigerant flowing out from one of the heat exchangers.

  As in the invention described in claim 19, in the ejector refrigeration cycle according to claim 17, one compression mechanism is the first compression mechanism (11a), and the refrigerant flow switching means (31, 32). ) Is switched to the refrigerant flow path for evaporating the refrigerant flowing out of the diffuser section (14d) in the outflow side heat exchanger (52) in one operation mode, and is switched to the outflow side heat exchanger (52) in the other operation mode. The first compression mechanism (11a) may be switched to a refrigerant flow path that radiates the discharged refrigerant.

  Further, as in the invention described in claim 20, in the ejector type refrigeration cycle described in claim 17, one compression mechanism is the second compression mechanism (21a), and the refrigerant flow switching means (31, 32). ) Is switched to the refrigerant flow path for evaporating the refrigerant flowing out of the diffuser section (14d) in the outflow side heat exchanger (52) in one operation mode, and is switched to the outflow side heat exchanger (52) in the other operation mode. Then, it may be switched to a refrigerant flow path for evaporating the refrigerant flowing out from one of the heat exchangers.

  According to a twenty-first aspect of the present invention, in the ejector refrigeration cycle according to any one of the sixteenth to twentieth aspects, a refrigerant that has flowed out of one heat exchanger and a second compression mechanism ( 21a) An internal heat exchanger for exchanging heat with the suction refrigerant is provided.

  According to this, in one operation mode, the enthalpy difference (refrigeration capacity) between the enthalpy of the other heat exchanger inlet-side refrigerant functioning as an evaporator and the enthalpy of the outlet-side refrigerant can be expanded, and COP can be improved.

  According to a twenty-second aspect of the present invention, in the ejector refrigeration cycle according to any one of the first to twenty-first aspects, the other of the first and second compression mechanisms (11a, 21a) in the other operation mode. The operation of the compression mechanism is stopped. Thereby, unnecessary driving power for driving the other compression mechanism can be reduced.

  According to a twenty-third aspect of the present invention, in the ejector refrigeration cycle according to any one of the first to twenty-second aspects, a high-pressure side pressure reducing means (19a) for decompressing and expanding the refrigerant flowing into the nozzle portion (13a) is provided. It is characterized by that.

  According to this, the refrigerant flowing into the nozzle part (13a) can be decompressed until it becomes a gas-liquid two-phase refrigerant by the action of the high-pressure side decompression means (19a). Therefore, compared with the case where the liquid refrigerant is introduced into the nozzle part (13a), the boiling of the refrigerant in the nozzle part (13a) can be promoted to improve the nozzle efficiency.

  As a result, the amount of pressure increase in the diffuser section (13d) can be increased to further improve the COP. In addition, nozzle efficiency is energy conversion efficiency at the time of converting the pressure energy of a refrigerant | coolant into a kinetic energy in a nozzle part (13a).

  Further, by configuring the high-pressure side pressure reducing means (19a) with a variable throttle mechanism, it is possible to change the flow rate of the refrigerant flowing into the nozzle portion (13a) according to the cycle load fluctuation. As a result, even when load fluctuation occurs, the cycle can be stably operated while exhibiting a high COP.

  According to a twenty-fourth aspect of the present invention, in the ejector refrigeration cycle according to any one of the first to twenty-third aspects, first discharge capacity changing means (11b) for changing the refrigerant discharge capacity of the first compression mechanism (11a). ) And second discharge capacity changing means (21b) for changing the refrigerant discharge capacity of the second compression mechanism (21a). The first discharge capacity changing means (11b) and the second discharge capacity changing means (21b) The refrigerant discharge capacities of the first compression mechanism (11a) and the second compression mechanism (21a) can be changed independently of each other.

  According to this, the refrigerant | coolant discharge capability of a 1st compression mechanism (11a) and the refrigerant | coolant discharge capability of a 2nd compression mechanism (21a) are adjusted independently, and either of a 1st, 2nd compression mechanism (11a, 21a) is adjusted. Can be operated while exhibiting high compression efficiency. Therefore, COP as the whole ejector type refrigerating cycle can be further improved.

  According to a twenty-fifth aspect of the present invention, in the ejector refrigeration cycle according to any one of the first to twenty-fourth aspects, the first compression mechanism (11a) and the second compression mechanism (21a) are in the same housing. It is accommodated and it is comprised integrally. Accordingly, the first compression mechanism (11a) and the second compression mechanism (21a) can be reduced in size, and the entire ejector refrigeration cycle can be reduced in size.

  As in the invention described in claim 26, in the ejector-type refrigeration cycle according to any one of claims 1 to 25, the first compression mechanism (11a) is configured to increase the pressure of the refrigerant until it becomes equal to or higher than the critical pressure. It may be.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a whole block diagram of the ejector-type refrigerating cycle of 1st Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode of the first embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode of the first embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 2nd Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 3rd Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode of the third embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode of the third embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 4th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode of the fourth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode of the fourth embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 5th Embodiment. (A) is the Mollier diagram which shows the state of the refrigerant | coolant of the cooling operation mode of 5th Embodiment, (b) is the Mollier diagram which shows the state of the refrigerant | coolant of the heating operation mode of 5th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 6th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode of the sixth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode of the sixth embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 7th Embodiment. (A) is a Mollier diagram which shows the state of the refrigerant | coolant of the cooling operation mode of 7th Embodiment, (b) is a Mollier diagram which shows the state of the refrigerant | coolant of the heating operation mode of 7th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 8th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode of the eighth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode of the eighth embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 9th Embodiment. (A) is a Mollier diagram which shows the state of the refrigerant | coolant of the cooling operation mode of 9th Embodiment, (b) is a Mollier diagram which shows the state of the refrigerant | coolant of the heating operation mode of 9th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 10th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode of the tenth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode of the tenth embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 11th Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 12th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode of the twelfth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode of the twelfth embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 13th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 14th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode of the fourteenth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode of the fourteenth embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 15th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode of the fifteenth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode of the fifteenth embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 16th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode of the sixteenth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode of the sixteenth embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 17th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode of the seventeenth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode of the seventeenth embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 18th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode of the eighteenth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode of the eighteenth embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 19th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode of the nineteenth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode of the nineteenth embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 20th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode of the twentieth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode of the twentieth embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 21st Embodiment. (A) is a Mollier diagram which shows the state of the refrigerant | coolant of the cooling operation mode of 21st Embodiment, (b) is the Mollier diagram which shows the state of the refrigerant | coolant of the heating operation mode of 21st Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 22nd Embodiment. (A) is a Mollier diagram which shows the state of the refrigerant | coolant of the cooling operation mode of 22nd Embodiment, (b) is a Mollier diagram which shows the state of the refrigerant | coolant of the heating operation mode of 22nd Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 23rd Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode of the 23rd embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode of the 23rd embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 24th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode of the twenty-fourth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode of the twenty-fourth embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 25th Embodiment. (A) is a Mollier diagram which shows the state of the refrigerant | coolant of the cooling operation mode of 25th Embodiment, (b) is a Mollier diagram which shows the state of the refrigerant | coolant of the heating operation mode of 25th Embodiment. (A) is a block diagram of the refrigerant | coolant flow path switching means in other embodiment, (b) is a block diagram of another refrigerant | coolant flow path switching means in other embodiment. It is a block diagram of another refrigerant flow path switching means in another embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of a prior art.

(First embodiment)
An example in which the ejector-type refrigeration cycle 100 of the present invention is applied to a cold storage container that keeps the internal temperature at a low temperature or a high temperature will be described with reference to FIGS. FIG. 1 is an overall configuration diagram of an ejector refrigeration cycle 100 of the present embodiment.

  The ejector refrigeration cycle 100 is configured to be switchable between a cooling operation mode for cooling the internal air that is a heat exchange target fluid and a heating operation mode for heating the internal air. In addition, the solid line arrow in FIG. 1 shows the flow of the refrigerant in the cooling operation mode, and the broken line arrow shows the flow of the refrigerant in the heating operation mode.

  In the ejector refrigeration cycle 100, the first compressor 11 sucks in refrigerant, compresses and discharges the refrigerant, and electrically compresses the first compression mechanism 11a having a fixed discharge capacity by the first electric motor 11b. Machine. Specifically, various compression mechanisms such as a scroll-type compression mechanism and a vane-type compression mechanism can be employed as the first compression mechanism 11a.

  The first electric motor 11b is controlled in its operation (number of rotations) by a control signal output from a control device described later, and may adopt either an AC motor or a DC motor. And the refrigerant | coolant discharge capability of the 1st compression mechanism 11a is changed by this rotation speed control. Therefore, the 1st electric motor 11b of this embodiment comprises the 1st discharge capability change means which changes the refrigerant discharge capability of the 1st compression mechanism 11a.

  A first electric four-way valve 31 is connected to the discharge port side of the first compressor 11 (first compression mechanism 11a). The first electric four-way valve 31 switches between the refrigerant flow path in the cooling operation mode and the refrigerant flow path in the heating operation mode, and the refrigerant flow whose operation is controlled by a control signal output from the control device. It is a path switching means.

  More specifically, the first electric four-way valve 31 is arranged between the discharge side of the first compressor 11 and the outdoor heat exchanger 41, the diffuser portion 13d outlet side of the ejector 13 described later, and the accumulator 14 inlet side described later. Between the refrigerant flow path (circuit shown by the solid line arrow in FIG. 1), the discharge side of the first compressor 11 and the outlet side of the diffuser portion 13d, and the inlet side of the outdoor heat exchanger 41 and the accumulator 14 Are switched to the refrigerant flow paths (circuits indicated by broken line arrows in FIG. 1) that are connected simultaneously.

  An outdoor heat exchanger 41 is connected to the discharge side of the first compressor 11 in the cooling operation mode via the first electric four-way valve 31 as in the refrigerant flow path indicated by the solid line arrow in FIG. . The outdoor heat exchanger 41 is a heat exchanger that exchanges heat between the refrigerant passing through the inside and the outdoor air blown by the blower fan 41a. The blower fan 41a is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the control device.

  Therefore, when the refrigerant discharged from the first compressor 11 having a temperature higher than the outside air temperature flows in the outdoor heat exchanger 41, the outdoor heat exchanger 41 functions as a radiator that radiates the refrigerant. Further, when the refrigerant flowing out of the fixed throttle 18 having a temperature lower than the outside air temperature flows in the outdoor heat exchanger 41, it functions as an evaporator for evaporating the refrigerant.

  In the ejector refrigeration cycle 100 of the present embodiment, a normal chlorofluorocarbon refrigerant is employed as the refrigerant, and a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant is configured. For this reason, the heat exchanger that functions as a radiator acts as a condenser that condenses the refrigerant.

  The refrigerant is mixed with refrigerating machine oil for lubricating the first compression mechanism 11a and the second compression mechanism 21a described later. This refrigerating machine oil is soluble in the liquid phase refrigerant and circulates through the cycle together with the refrigerant.

  Furthermore, one refrigerant inflow / outlet of the electric three-way valve 33 is connected to the outlet side of the outdoor heat exchanger 41 in the cooling operation mode. The electric three-way valve 33 switches the refrigerant channel in the cooling operation mode and the refrigerant channel in the heating operation mode, and constitutes a refrigerant channel switching means together with the first electric four-way valve 31 and the like. The operation of the electric three-way valve 33 is controlled by a control signal output from the control device.

  Specifically, the electric three-way valve 33 includes a refrigerant flow path (a circuit indicated by a solid line arrow in FIG. 1) that connects between the outdoor heat exchanger 41 and the nozzle portion 13a inlet side of the ejector 13, and will be described later. The refrigerant flow path (circuit indicated by the broken line arrow in FIG. 1) that connects the outlet side of the fixed throttle 18 and the outdoor heat exchanger 41 is switched.

  Further, in the electric three-way valve 33, when the one refrigerant flow path is switched, the other refrigerant flow path is closed. Therefore, the refrigerant does not flow through the other refrigerant flow path, and the refrigerant does not leak from the inside of the cycle to the outside.

  The ejector 13 is a refrigerant decompression unit that decompresses and expands the refrigerant, and is also a refrigerant circulation unit that circulates the refrigerant by suction of a refrigerant flow ejected at high speed.

  More specifically, the ejector 13 squeezes the passage area of the high-pressure refrigerant flowing out of the outdoor heat exchanger 41 in the cooling operation mode to reduce the pressure of the high-pressure refrigerant in an isentropic manner. The refrigerant suction port 13b is disposed so as to communicate with the refrigerant injection port and sucks the refrigerant discharged from the second compressor 21 described later.

  Furthermore, a mixing portion 13c that mixes the high-speed refrigerant flow ejected from the nozzle portion 13a and the suction refrigerant from the refrigerant suction port 13b is provided in the refrigerant flow downstream portion of the nozzle portion 13a and the refrigerant suction port 13b. A diffuser portion 13d forming a pressure increasing portion is provided on the refrigerant flow downstream side of the mixing portion 13c.

  The diffuser portion 13d is formed in a shape that gradually increases the refrigerant passage area, and functions to increase the refrigerant pressure by decelerating the refrigerant flow, that is, to convert the velocity energy of the refrigerant into pressure energy. Further, as described above, one refrigerant inflow / outlet of the first electric four-way valve 31 is connected to the outlet side of the diffuser portion 13d.

  The accumulator 14 is a gas-liquid separator that separates the gas-liquid refrigerant flowing into the accumulator 14 and accumulates excess liquid-phase refrigerant in the cycle. Therefore, the accumulator 14 of the present embodiment separates the gas / liquid refrigerant flowing out of the diffuser portion 13d in the cooling operation mode, and separates the gas / liquid refrigerant flowing out of the outdoor heat exchanger 41 in the heating operation mode.

  The gas-phase refrigerant outlet of the accumulator 14 is connected to the inlet of the first compressor 11, and the liquid-phase refrigerant outlet is connected to the three-way joint 17a via the separation refrigerant fixed throttle 15 and the check valve 16a. One refrigerant inflow / outlet is connected.

  The separation refrigerant fixed throttle 15 is a separation refrigerant decompression unit that further decompresses and expands the refrigerant flowing out of the accumulator 14. As the separation refrigerant fixed throttle 15, specifically, an orifice or a capillary tube can be adopted. Further, the check valve 16a only allows the refrigerant to flow from the liquid refrigerant outlet side of the accumulator 14 to the three-way joint 17a side.

  The three-way joint 17a is a refrigerant pipe joint member having three refrigerant inflow / outlets communicating with each other. In addition, the use side heat exchanger 51 and the inlet side of the fixed throttle 18 as the refrigerant pressure reducing means are connected to another refrigerant inflow / outlet of the three-way joint 17a. The basic configuration of the fixed throttle 18 is the same as that of the separated refrigerant fixed throttle 15. Further, as described above, one refrigerant inlet / outlet of the electric three-way valve 33 is connected to the outlet side of the fixed throttle 18.

  The use side heat exchanger 51 is a heat exchanger that exchanges heat between the refrigerant passing through the inside and the internal air that is the heat exchange target fluid circulated and blown by the blower fan 51a. The blower fan 51a is an electric blower in which the rotation speed (amount of blown air) is controlled by a control voltage output from the control device.

  Accordingly, the use side heat exchanger 51 functions as an evaporator for evaporating the refrigerant when the refrigerant flowing out of the branch refrigerant fixed throttle 15 flows from the inside air in the use side heat exchanger 51 rather than the inside air. When the refrigerant discharged from the first compressor 11 having a temperature higher than that of the internal air flows in the exchanger 51, it functions as a radiator that radiates heat from the refrigerant.

  One refrigerant inlet / outlet of the second electric four-way valve 32 is connected to the other refrigerant inlet / outlet of the use side heat exchanger 51. The second electric four-way valve 32 switches the refrigerant flow path in the cooling operation mode and the refrigerant flow path in the heating operation mode, and constitutes a refrigerant flow switching means together with the first electric four-way valve 31 and the like. The basic configuration of the second electric four-way valve 32 is the same as that of the first electric four-way valve 31.

  More specifically, the second electric four-way valve 32 is provided between the use-side heat exchanger 51 and the second compressor 21 suction port side and between the second compressor 21 discharge port side and the refrigerant suction port 13b of the ejector 13. Between the refrigerant flow path (circuit indicated by the solid line arrow in FIG. 1), the refrigerant suction port 13b side and the use side heat exchanger 51, and between the discharge port and the suction port of the second compressor 21. Are switched to the refrigerant flow paths (circuits indicated by broken line arrows in FIG. 1).

  The second compressor 21 sucks, compresses and discharges the refrigerant, and its basic configuration is the same as that of the first compressor 11. Accordingly, the second compressor 21 is an electric compressor that drives the fixed capacity type second compression mechanism 21a by the second electric motor 21b. Furthermore, the second electric motor 21b of the present embodiment constitutes a second discharge capacity changing means for changing the refrigerant discharge capacity of the second compression mechanism 21a.

  A control device (not shown) includes a known microcomputer including a CPU, a ROM, a RAM, and the like and peripheral circuits thereof. This control device performs various calculations and processes based on the control program stored in the ROM, and controls the operation of the various electric actuators 11b, 21b, 31, 32, 33, 41a, 51a, etc. To do.

  Therefore, this control device functions as a first discharge capacity control means for controlling the operation of the first electric motor 11b as the first discharge capacity change means, and operates as the second electric motor 21b as the second discharge capacity change means. Function as second discharge capacity control means for controlling the flow rate, and refrigerant flow path switching control means for controlling the operation of the first and second electric four-way valves 31, 32 and electric three-way valve 33 which are flow path switching means Have both. Of course, the first discharge capacity control means, the second discharge capacity control means, and the refrigerant flow path switching control means may be configured by different control devices.

  In addition, the control device includes an outside air sensor that detects the outside air temperature, a detection value of a sensor group (not shown) such as an inside temperature sensor that detects the inside temperature, an operation switch that operates the cold storage chamber, and cools the inside air. Various operation signals of an operation panel (not shown) provided with a mode changeover switch between a cooling operation mode for heating and a heating operation mode for heating the internal air are input.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. 2A is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 2B is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, the cooling operation mode will be described. The cooling operation mode is executed when the operation switch of the operation panel is turned on and the cooling operation mode is selected by the mode changeover switch. In the cooling operation mode, the control device operates the first and second electric motors 11b and 21b, the blower fans 41a and 51a, and the first and second electric four-way valves 31 and 32 and the electric three-way valve 33 are shown as solid lines. Switch to the circuit indicated by the arrow.

  Thereby, the first compressor 11 (→ first electric four-way valve 31) → outdoor heat exchanger 41 (→ electric three-way valve 33) → nozzle portion 13a of the ejector 13 (→ first electric four-way valve 31) → The refrigerant circulates in the order of accumulator 14 → first compressor 11, and accumulator 14 → separated refrigerant fixed throttle 15 (→ check valve 16a → three-way joint 17a) → use side heat exchanger 51 (→ second electric four-way valve). 32) → the second compressor 21 (→ the second electric four-way valve 32) → the refrigerant suction port 13b of the ejector 13 (→ the first electric four-way valve 31) → the cycle in which the refrigerant circulates is configured in this order. .

Therefore, the refrigerant compressed by the first compressor 11 (first compression mechanism 11 a) (point a _{2 in} FIG. 2A) is transferred to the outdoor heat exchanger 41 via the first electric four-way valve 31. It flows in, exchanges heat with outside air (outside air) blown from the blower fan 41a, dissipates heat, and condenses (a ₂ points → b ₂ points). That is, in the cooling operation mode of this embodiment, the outdoor heat exchanger 41 functions as a radiator.

The refrigerant radiated by the outdoor heat exchanger 41 flows into the nozzle portion 13a of the ejector 13 via the electric three-way valve 33, and isentropically decompressed and expanded (b ₂ point → c ₂ point). And the pressure energy of a refrigerant | coolant is converted into speed energy at the time of this decompression | expansion expansion, and a refrigerant | coolant is injected at high speed from the refrigerant | coolant injection port of the nozzle part 13a.

Due to the refrigerant suction action of the injected refrigerant, the refrigerant discharged from the second compressor 21 (second compression mechanism 21a) (j ₂ points) is passed from the refrigerant suction port 13b to the inside of the ejector 13 via the second electric four-way valve 32. Sucked. Furthermore, the refrigerant injected from the nozzle portion 13a and the suction refrigerant sucked from the refrigerant suction port 13b are mixed in the mixing portion 13c of the ejector 13 and flow into the diffuser portion 13d (c ₂ point → d ₂ point and j ₂ points → d ₂ points).

In the diffuser portion 13d, the refrigerant pressure energy rises (d ₂ point → e ₂ point) because the velocity energy of the refrigerant is converted into pressure energy due to the expansion of the passage area. The refrigerant that has flowed out of the diffuser portion 13d flows into the accumulator 14 via the first electric four-way valve 31, and is separated into a gas phase refrigerant and a liquid phase refrigerant (e ₂ point → f ₂ point and e ₂ point → g ₂ points).

The gas-phase refrigerant flowing out from the gas-phase refrigerant outlet of the accumulator 14 is sucked into the first compressor 11 and compressed (f ₂ point → a ₂ point). On the other hand, the liquid-phase refrigerant that has flowed out from the liquid-phase refrigerant outlet of the accumulator 14 is further decompressed and expanded in an isoenthalpy manner at the separation refrigerant fixed throttle 15 to reduce its pressure (g ₂ point → h ₂ point).

The refrigerant expanded under reduced pressure by the separation refrigerant fixed throttle 15 flows into the use side heat exchanger 51 through the check valve 16a and the three-way joint 17a, and absorbs heat from the internal air circulated and blown by the blower fan 51a. Evaporate (h ₂ point → i ₂ point). Thereby, the internal air which is a fluid for heat exchange is cooled.

  That is, in the cooling operation mode of the present embodiment, the use side heat exchanger 51 functions as an evaporator. Furthermore, in the cooling operation mode of the present embodiment, since the electric three-way valve 33 is switched to the refrigerant flow path that connects the outdoor heat exchanger 41 and the nozzle portion 13a inlet side of the ejector 13, the three-way joint 17a The refrigerant that flows into the fixed throttle 18 does not flow out to the fixed throttle 18 side.

The refrigerant flowing out from the use side heat exchanger 51 is sucked into the second compressor 21 through the second electric four-way valve 32 and compressed (i ₂ point → j ₂ point). At this time, the control device controls the operations of the first and second electric motors 11b and 21b so that the COP of the ejector refrigeration cycle as a whole approaches a maximum.

  Specifically, in order to improve the mechanical efficiency of the first and second compression mechanisms 11a and 21a, the first and second compression mechanisms 11a and 21a are controlled so that the pressure increase amounts are substantially equal. Note that the compression efficiency means that the increase amount ΔH1 is actually calculated when the increase amount of the enthalpy of the refrigerant when the refrigerant is isentropically compressed by the first and second compressors 11 and 21 is ΔH1. 1 and a value obtained by dividing the refrigerant by the enthalpy increase ΔH2 of the refrigerant when the refrigerant is pressurized by the second compressors 11 and 21.

  For example, when the rotation speed or the pressure increase amount (pressure difference between the discharge pressure and the suction pressure) of the first and second compressors 11 and 21 increases, the temperature of the refrigerant rises due to the frictional heat, and the actual enthalpy increase ΔH2 Increases the compression efficiency.

Further, as described above, the refrigerant discharged from the second compressor 21 is sucked into the ejector 13 from the refrigerant suction port 13b via the second electric four-way valve 32 (j ₂ point → d ₂ point). .

  Next, the heating operation mode will be described. The heating operation mode is executed when the heating operation mode is selected by the mode switching switch in a state where the operation switch of the operation panel is turned on. In the heating operation mode, the control device operates the first electric motor 11b and the blower fans 41a and 51a, and switches the first and second electric four-way valves 31 and 32 and the electric three-way valve 33 to a circuit indicated by a broken line arrow. At the same time, the second electric motor 21b is stopped.

  That is, in this embodiment, since the second compression mechanism 21a is not driven by the second electric motor 21b, the second compressor 21 does not suck in the refrigerant, compresses and discharges it, and only the first compressor 11 has. The refrigerant is sucked, compressed and discharged. Therefore, in this embodiment, the 1st compression mechanism 11a respond | corresponds to one compression mechanism described in the claim.

  Thus, the first compressor 11 (→ first electric four-way valve 31 → diffuser portion 13d of the ejector 13 → second electric four-way valve 32) → use side heat exchanger 51 → fixed throttle 18 (→ electric three-way valve) 33) → Outdoor heat exchanger 41 (→ first electric four-way valve 31) → accumulator 14 → first compressor 11 in this order.

Accordingly, the refrigerant compressed by the first compressor 11 (point k _{2 in} FIG. 2B) flows into the ejector 13 from the diffuser portion 13d of the ejector 13 through the first electric four-way valve 31. . Furthermore, in the heating operation mode, the electric three-way valve 33 is switched to the refrigerant flow path connecting the outlet side of the fixed throttle 18 and the outdoor heat exchanger 41, so that the refrigerant flowing into the ejector 13 It does not flow into the side of 13a, but its entire flow rate flows out of the refrigerant suction port 13b.

That is, in the heating operation mode, the refrigerant flow in the ejector 13 flows backward with respect to the cooling operation mode. Further, the refrigerant flowing through the ejector 13 is slightly reduced in pressure by the pressure loss when passing through the diffuser portion 13d → the refrigerant suction port 13b (k ₂ point → m ₂ point). The refrigerant flowing out from the refrigerant suction port 13b of the ejector 13 flows into the use side heat exchanger 51 through the second electric four-way valve 32.

The refrigerant that has flowed into the use side heat exchanger 51 exchanges heat with the inside air circulated from the blower fan 51a to dissipate heat and condense (m ₂ point → n ₂ point). As a result, the internal air is heated. That is, in the heating operation mode, the use side heat exchanger 51 functions as a radiator. The refrigerant radiated by the use side heat exchanger 51 flows into the fixed throttle 18 through the three-way joint 17a and is decompressed and expanded in an enthalpy manner (n ₂ point → o ₂ point).

  In the present embodiment, the refrigerant flowing into the three-way joint 17a does not flow out to the separated refrigerant pressure reducing means 15 side by the action of the check valve 16a, and the entire flow rate is decompressed and expanded by the fixed throttle 18. .

The refrigerant expanded under reduced pressure by the fixed throttle 18 flows into the outdoor heat exchanger 41 through the electric three-way valve 33, absorbs heat from the outside air (outside air) blown by the blower fan 41a, and evaporates. That is, in the cooling operation mode of this embodiment, the outdoor heat exchanger 41 functions as an evaporator. Furthermore, the refrigerant that has flowed out of the outdoor heat exchanger 41 flows into the accumulator 14 via the first electric four-way valve 31 and is separated into gas and liquid (point o ₂ → point p ₂ ).

The gas-phase refrigerant flowing out from the gas-phase refrigerant outlet of the accumulator 14 is sucked into the first compressor 11 and compressed (p ₂ point → k ₂ point). In the heating operation mode, among the refrigerant pressures acting on the valve body of the check valve 16a, the refrigerant pressure on the separated refrigerant fixed throttle 15 side is lower than the refrigerant pressure on the three-way joint 17a side.

  Therefore, the check valve 16a is closed, and the liquid refrigerant in the accumulator 14 does not flow out to the separated refrigerant fixed throttle 15 side. Other operations are the same as those in the cooling operation mode.

  Therefore, when the ejector refrigeration cycle 100 of this embodiment is operated, in the cooling operation mode, an ejector refrigeration cycle in which the outdoor heat exchanger 41 functions as a radiator and the use side heat exchanger 51 functions as an evaporator is provided. Composed. Thereby, the inside air can be cooled by the use side heat exchanger 51.

  In the heating operation mode, the refrigerant discharged from the first compressor 11 (first compression mechanism 11a) is radiated by the use-side heat exchanger 51, and the radiated refrigerant is decompressed and expanded by the fixed throttle 18, and is decompressed and expanded. Is re-evaporated by the outdoor heat exchanger 41, and a refrigeration cycle is constructed in which the evaporated refrigerant is again pressurized by the first compressor 11 (first compression mechanism 11a). Thereby, the internal air can be heated by the use side heat exchanger 51.

  Furthermore, in the ejector refrigeration cycle 100 of the present embodiment, the following excellent effects can be obtained.

  (A) In the cooling operation mode, the ejector-type refrigeration cycle can be stably operated even if the operating condition is such that the drive flow of the ejector 13 decreases.

  That is, since the second compressor 21 (second compression mechanism 21a) is provided, the pressure difference between the high-pressure refrigerant and the low-pressure refrigerant is reduced, for example, at a low outside air temperature, and the drive flow of the ejector 13 is reduced. Even if the operating condition is such that the flow rate of the ejector 13 decreases, that is, the operating condition that the suction capacity of the ejector 13 decreases, the suction capacity of the ejector 13 can be assisted by the suction and discharge action of the second compression mechanism 21a. .

  Furthermore, in the cycle configuration of the present embodiment, the liquid refrigerant can be reliably supplied from the accumulator 14 to the use side heat exchanger 51 by the suction action of the second compression mechanism 21a. As a result, the ejector-type refrigeration cycle can be stably operated even in the cooling operation mode even if the operating condition is such that the suction capacity of the ejector 13 is reduced.

  (B) In the cooling operation mode, the pressure of the refrigerant can be increased by the pressure increasing action of the two first and second compression mechanisms 11a, 21a and the diffuser portion 13d of the ejector 13, so that the pressure of the refrigerant is increased by one compression mechanism. Thus, the COP can be improved by reducing the driving power of the first and second compression mechanisms 11a and 21a.

  That is, the driving power of the first compression mechanism 11a can be reduced by increasing the suction pressure of the first compression mechanism 11a by the pressure increasing action of the diffuser portion 13d. Furthermore, since the pressure difference between the suction pressure and the discharge pressure in the first and second compression mechanisms 11a and 21a can be reduced, the compression efficiency of the first and second compression mechanisms 11a and 21a can be improved.

  At this time, since the first and second electric motors 11b and 21b can independently change the refrigerant discharge capacities of the first and second compression mechanisms 11a and 21a, COP is effectively reduced as the entire ejector refrigeration cycle 100. Can be improved.

  The refrigeration cycle apparatus having a large pressure difference between the high-pressure refrigerant and the low-pressure refrigerant is capable of stably operating the cycle while exhibiting a high COP during the cooling operation mode in which the ejector refrigeration cycle is configured as in this embodiment. For example, it is extremely effective when the internal temperature is lowered to a very low temperature (for example, about −30 ° C. to −10) in the cooling operation mode.

  (C) In the heating operation mode, a vapor compression refrigeration cycle (heat pump cycle) that does not use the ejector 13 as a refrigerant decompression means can be configured. Therefore, the operation of the cycle becomes unstable due to a decrease in the suction capacity of the ejector 13. There is no end. Therefore, the cycle can be stably operated even in the heating operation mode.

  (D) Since the second electric motor 21b is stopped in the heating operation mode, unnecessary driving power for driving the second compression mechanism 21a can be reduced. (E) In any of the operation modes, the first compressor 11 can suck the gas-phase refrigerant separated by the accumulator 14, so that the problem of liquid compression of the first compressor 11 can be avoided. .

(Second Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 3, the electric three-way valve 33 is eliminated from the ejector refrigeration cycle 100 of the first embodiment, and the second three-way joint 17b and the second, second, An example in which three check valves 16b and 16c are provided will be described. In FIG. 3, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.

  The basic configuration of the second three-way joint 17b is the same as that of the three-way joint 17a of the first embodiment. The three refrigerant inlets and outlets of the second three-way joint 17b are respectively connected to the outdoor heat exchanger 41, the nozzle 13a inlet side of the ejector 13 and the fixed throttle 18 outlet, similarly to the electric three-way valve 33 of the first embodiment. The side is connected.

  The second check valve 16b is arranged between the second three-way joint 17b and the nozzle part 13a inlet side of the ejector 13, and only allows the refrigerant to flow from the second three-way joint 17b side to the nozzle part 13a inlet side. ing. The third check valve 16c is arranged between the second three-way joint 17b and the fixed throttle 18 outlet side, and only allows the refrigerant to flow from the fixed throttle 18 outlet side to the second three-way joint 17b. .

  In the following description, in order to clarify the difference between the three-way joint 17a and the second three-way joint 17b, the three-way joint 17a is described as the first three-way joint 17a, and the check valve 16a and the second and third reverse valves are described. In order to clarify the difference from the stop valves 16b and 16c, the check valve 16a is described as a first check valve 16a. Other configurations are the same as those of the first embodiment.

  Next, the operation of this embodiment in the above configuration will be described. In the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a and 51a, and the first and second electric four-way valves 31 and 32 are indicated by solid arrows. Switch to the circuit shown.

  Thereby, the first compressor 11 (→ first electric four-way valve 31) → outdoor heat exchanger 41 (→ second three-way joint 17b → second check valve 16b) → nozzle portion 13a of the ejector 13 (→ first The refrigerant circulates in the order of electric four-way valve 31) → accumulator 14 → first compressor 11 and accumulator 14 → separated refrigerant fixed throttle 15 (→ first check valve 16a → three-way joint 17a) → use side heat exchanger. 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → refrigerant suction port 13b of ejector 13 (→ first electric four-way valve 31) → accumulator 14 A cycle in which the refrigerant circulates is configured.

  Therefore, the refrigerant discharged from the first compressor 11 flows in exactly the same way as the cooling operation mode of the first embodiment, flows into the outdoor heat exchanger 41, and dissipates heat. The refrigerant that has flowed out of the outdoor heat exchanger 41 flows into the second three-way joint 17b, and then flows into the nozzle portion 13a of the ejector 13 through the second check valve 16b.

  At this time, the refrigerant flowing into the second three-way joint 17b does not flow out to the outlet side of the fixed throttle 18 due to the action of the third check valve 16c, and its entire flow rate flows into the nozzle portion 13a of the ejector 13. Other operations are the same as in the refrigerant operation mode of the first embodiment.

  That is, in the cooling operation mode of the present embodiment, a cycle similar to that in the cooling operation mode of the first embodiment is configured, and operates as shown in the Mollier diagram of FIG. 2A of the first embodiment. As a result, in the cooling operation mode of the present embodiment, it is possible to obtain the same effect as the cooling operation mode of the first embodiment.

  On the other hand, in the heating operation mode, the control device operates the first electric motor 11b and the blower fans 41a and 51a to switch the first and second electric four-way valves 31 and 32 to the circuit indicated by the broken-line arrow, and the second The electric motor 21b is stopped.

  Accordingly, the first compressor 11 (→ first electric four-way valve 31 → diffuser portion 13d of the ejector 13 → second electric four-way valve 32) → use side heat exchanger 51 → fixed throttle 18 (→ third check) A cycle in which the refrigerant circulates in the order of the valve 16c → the second three-way joint 17b) → the outdoor heat exchanger 41 (→ the first electric four-way valve 31) → the accumulator 14 → the first compressor 11.

  Therefore, the refrigerant discharged from the first compressor 11 flows in the same manner as in the heating operation mode of the first embodiment, flows into the fixed throttle 18 and is decompressed and expanded. The refrigerant that has flowed out of the fixed throttle 18 flows into the outdoor heat exchanger 41 through the third check valve 16c and the second three-way joint 17b.

  In the heating operation mode, among the refrigerant pressures acting on the valve body portion of the second check valve 16b, the refrigerant pressure on the second three-way joint 17b side is lower than the refrigerant pressure on the nozzle portion 13a side of the ejector 13. Therefore, the second check valve 16b is closed, and the refrigerant that has flowed into the second three-way joint 17b does not flow out to the nozzle portion 13a side, but its entire flow rate flows out to the outdoor heat exchanger 41 side. Other operations are the same as those in the heating operation mode of the first embodiment.

  That is, in the heating operation mode of the present embodiment, a cycle similar to that in the heating operation mode of the first embodiment is configured, and operates as shown in the Mollier diagram of FIG. 2B of the first embodiment. As a result, in the heating operation mode of the present embodiment, the same effect as that of the heating operation mode of the first embodiment can be obtained.

  Further, in the present embodiment, the electric three-way valve 33 is eliminated, and the second and third check valves 16b and 16c configured by a pure mechanical mechanism are employed to switch between the cooling operation mode and the heating operation mode. Since possible cycles are configured, the same effects as those of the first embodiment can be obtained with a simple cycle configuration.

(Third embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 4, the connection mode of each component device is changed with respect to the ejector refrigeration cycle 100 of the first embodiment, and the second compressor is changed in the heating operation mode. An example in which the refrigerant is switched to a cycle in which the refrigerant is compressed and discharged by 21 (second compression mechanism 21a) will be described.

  Specifically, the first electric four-way valve 31 of the present embodiment is provided between the discharge side of the first compressor 11 and the outdoor heat exchanger 41, the outlet side of the diffuser portion 13d of the ejector 13, and the inlet side of the accumulator 14. Between the refrigerant flow path (circuit indicated by the solid arrow in FIG. 4), the discharge side of the first compressor 11 and the inlet side of the accumulator 14, and the diffuser portion 13d of the outdoor heat exchanger 41 and the ejector 13 The refrigerant flow path (circuit indicated by the broken line arrow in FIG. 4) that connects the outlet side at the same time is switched.

  In addition, the second electric four-way valve 32 is provided between the use-side heat exchanger 51 and the second compressor 21 suction port side and between the second compressor 21 discharge port side and the refrigerant suction port 13b side of the ejector 13 at the same time. The refrigerant flow path (circuit shown by the solid line arrow in FIG. 4) to be connected, between the second compressor 21 discharge port side and the use side heat exchanger 51, the refrigerant suction port 13b side, and the second compressor 21 suction port side. Are switched to the refrigerant flow paths (circuits indicated by broken line arrows in FIG. 4) that are simultaneously connected to each other.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 5 (a) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 5 (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  Moreover, the code | symbol which shows the state of the refrigerant | coolant in FIG. 5 uses the same code | symbol as the code | symbol which shows the state of the same refrigerant | coolant in FIG. 2, and has changed only the subscript. The same applies to the Mollier diagram in the following embodiments.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a and 51a, and the first and second electric four-way valves 31 and 32, the electric The three-way valve 33 is switched to a circuit indicated by a solid arrow.

  Thereby, as shown by the solid line arrow in FIG. 4, the first compressor 11 (→ the first electric four-way valve 31) → the outdoor heat exchanger 41 (→ the electric three-way valve 33) → the nozzle portion 13 a of the ejector 13 ( → First electric four-way valve 31) → Accumulator 14 → First compressor 11 circulates refrigerant in this order, and accumulator 14 → separated refrigerant fixed throttle 15 (→ check valve 16a → three-way joint 17a) → use side heat exchange 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → refrigerant suction port 13b of ejector 13 (→ first electric four-way valve 31) → accumulator 14 A cycle in which the refrigerant circulates in sequence.

  That is, in the cooling operation mode of the present embodiment, a cycle similar to that of the cooling operation mode of the first embodiment is configured and operates as shown in the Mollier diagram of FIG. The operation in the cooling operation mode is the same as the operation in the cooling operation mode of the first embodiment (FIG. 5B). Therefore, in the cooling operation mode of the present embodiment, the same effect as that of the cooling operation mode of the first embodiment can be obtained.

  Next, in the heating operation mode, the control device operates the second electric motor 21b and the blower fans 41a and 51a, and the first and second electric four-way valves 31 and 32 and the electric three-way valve 33 are indicated by broken line arrows. While switching to a circuit, the 1st electric motor 11b is stopped.

  That is, in this embodiment, since the first compression mechanism 21a is not driven by the first electric motor 11b, the first compressor 11 does not suck in the refrigerant, compresses and discharges it, and only the second compressor 21 The refrigerant is sucked, compressed and discharged. Therefore, in this embodiment, the 2nd compression mechanism 21a respond | corresponds to one compression mechanism described in the claim.

  Accordingly, the second compressor 21 (→ second electric four-way valve 32) → the use-side heat exchanger 51 → fixed throttle 18 (→ electric three-way valve 33) → outdoor heat exchanger 41 (→ first electric four-way valve) A cycle in which the refrigerant circulates in the order of the valve 31) → the diffuser portion 13d of the ejector 13 (→ the second electric four-way valve 32) → the second compressor 21.

Therefore, the refrigerant (the point l _{5 in} FIG. 5B) compressed by the second compressor 21 flows into the use side heat exchanger 51 via the second electric four-way valve 32. The refrigerant that has flowed into the use side heat exchanger 51 exchanges heat with the internal air circulated from the blower fan 51a to dissipate heat and condense (l ₅ points → n ₅ points). As a result, the internal air is heated.

The refrigerant radiated by the use side heat exchanger 51 flows into the fixed throttle 18 via the first three-way joint 17a and is decompressed and expanded in an enthalpy manner, similarly to the heating operation mode of the first embodiment ( n ₅ points → o ₅ points). Furthermore, the refrigerant expanded under reduced pressure by the fixed throttle 18 flows into the outdoor heat exchanger 41 via the electric three-way valve 32 and evaporates (o ₅ point → p ₅ point).

Then, the refrigerant flowing out of the outdoor heat exchanger 41 flows into the ejector 13 from the diffuser portion 13d of the ejector 13 via the first electric four-way valve 31, and is slightly due to pressure loss when flowing back in the ejector 13. (P ₅ point → m ₅ point) and flows out from the refrigerant suction port 13 b of the ejector 13. The refrigerant flowing out from the refrigerant suction port 13b is sucked into the second compressor 11 through the second electric four-way valve 32 and compressed (m ₅ point → l ₅ point).

  Therefore, in the heating operation mode of the present embodiment, the refrigerant discharged from the second compressor 21 (second compression mechanism 21a) is radiated by the use side heat exchanger 51, and the radiated refrigerant is decompressed and expanded by the fixed throttle 18, A refrigerant cycle in which the refrigerant expanded under reduced pressure is evaporated by the outdoor heat exchanger 41 and the evaporated refrigerant is increased again by the second compressor 11 (second compression mechanism 21a) is configured.

  That is, in the heating operation mode of the present embodiment, the second compressor 21 fulfills the function of the first compressor 11 in the first embodiment, so that the cycle is substantially the same as in the heating operation mode of the first embodiment. Can be configured. As a result, the inside air can be heated by the use side heat exchanger 51, and the same effect as the heating operation mode of the first embodiment can be obtained.

(Fourth embodiment)
An example in which the ejector-type refrigeration cycle 200 of the present invention is applied to a cold storage container that keeps the internal temperature at a low temperature or a high temperature will be described with reference to FIGS. The cold storage in this embodiment has a first storage capable of switching between cold storage and a second storage (refrigerator) capable of only low temperature storage. FIG. 6 is an overall configuration diagram of the ejector refrigeration cycle 200 of the present embodiment.

  The ejector refrigeration cycle 200 is obtained by changing the components and the connection mode thereof, that is, changing the cycle configuration with respect to the ejector refrigeration cycle 100 of the first embodiment, which is the premise thereof.

  As shown in FIG. 6, in the ejector refrigeration cycle 200 of the present embodiment, the accumulator 14, the separation refrigerant fixed throttle 15, the first check valve 16a, and the first three-way joint 17a are abolished with respect to the first embodiment. ing. An outflow side heat exchanger 52 is provided between one refrigerant inflow / outlet of the first electric four-way valve 31 and the first compressor 11 suction side.

  The outflow side heat exchanger 52 is a heat exchanger for heat absorption that evaporates by allowing the refrigerant passing therethrough to exchange heat with the air in the second storage box that is circulated and blown by the blower fan 52a, thereby exerting an endothermic effect. . The blower fan 52a is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the control device.

  In this embodiment, since the outflow side heat exchanger 52 is provided, the first electric four-way valve 31 is provided between the discharge port side of the first compressor 11 and the outdoor heat exchanger 41 and the diffuser portion 13d of the ejector 13. Between the refrigerant flow path (circuit shown by the solid line arrow in FIG. 6) that connects the outlet side and the outlet side heat exchanger 52 inlet side at the same time, between the discharge side of the first compressor 11 and the outlet side of the diffuser portion 13d And the refrigerant | coolant flow path (circuit shown by the broken-line arrow of FIG. 6) which connects between the outdoor heat exchanger 41 and the outflow side heat exchanger 52 entrance side simultaneously is switched.

  Furthermore, in this embodiment, the electric three-way valve 33 is abolished, and the high-pressure side electric expansion valve 19a is connected to the outlet side of the outdoor heat exchanger 41 in the cooling operation mode. The high-pressure side electric expansion valve 19a is a high-pressure side decompression unit that decompresses the refrigerant flowing into the nozzle portion 13a of the ejector 13 until the gas-liquid two-phase state is achieved in the cooling operation mode.

  Specifically, the high-pressure side electric expansion valve 19a includes a valve body configured to be able to change the throttle opening, and an electric actuator including a stepping motor that changes the throttle opening of the valve body. Variable aperture mechanism. Furthermore, the valve opening degree of the high pressure side electric expansion valve 19a is controlled by the control signal of the control device so that the degree of superheat of the refrigerant sucked in the first compressor 11 becomes a predetermined value.

  At the outlet side of the high pressure side electric expansion valve 19a in the cooling operation mode, the flow of the refrigerant flowing out from the high pressure side electric expansion valve 19a is branched, and one of the branched refrigerants is directed to the nozzle portion 13a side of the ejector 13. An upstream branching section 22 is connected to flow out and flow out the other refrigerant to the fixed throttle 18 side.

  The upstream branch portion 22 has the same structure as the three-way joint, and may be configured by joining pipes having different pipe diameters, or by providing a plurality of refrigerant passages having different passage diameters in a metal block or resin block. It may be configured. Further, a second check valve 16b similar to that of the second embodiment is disposed between the upstream branch portion 22 and the nozzle portion 13a side.

  In the present embodiment, since the first three-way joint 17a is eliminated, the fixed throttle 18 outlet side in the cooling operation mode (fixed throttle 18 inlet side in the heating operation mode) and the use side heat exchanger 52 in the cooling operation mode. The inlet side (the use side heat exchanger 52 inlet side in the heating operation mode) is connected. Other configurations are the same as those of the first embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 7A is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 7B is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a, 51a, and 52a, and the first and second electric four-way valves 31 and 32 are operated. The circuit is switched to the circuit indicated by the solid arrow, and the high-pressure electric expansion valve 19a is in the throttle state.

  Thereby, as shown by the solid line arrow in FIG. 6, the first compressor 11 (→ the first electric four-way valve 31) → the outdoor heat exchanger 41 → the high-pressure side electric expansion valve 19 a → the upstream branch portion 22 (→ The refrigerant circulates in the order of the second check valve 16b) → the nozzle part 13a of the ejector 13 (→ the first electric four-way valve 31) → the outflow side heat exchanger 52 → the first compressor 11, and the upstream side branch part 22 → Fixed throttle 18 → Use side heat exchanger 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → refrigerant suction port 13b of the ejector 13 (→ first electric A cycle in which the refrigerant circulates in the order of the four-way valve 31) → the outflow side heat exchanger 52 → the first compressor 11.

Therefore, (a _7-point in FIG. 7 (a)) the refrigerant compressed in the first compressor 11 flows into the outdoor heat exchanger 41 via the first electric four-way valve 31, the blower from the blower fan 41a The heat is exchanged with the outside air (outside air) that has been discharged to condense and dissipate heat (a ₇ points → b ₇ points). The refrigerant flowing out from the outdoor heat exchanger 41, is isenthalpic depressurize inflated to an intermediate pressure and flows into the high-pressure side electric expansion valve 19a, a gas-liquid two-phase state (b ₇ points → b _'7 point).

At this time, the valve opening degree of the high-pressure side electric expansion valve 19a, the first compressor 11 the degree of superheat of the refrigerant on the suction side (f ₇ points) is adjusted to be predetermined value. The intermediate-pressure refrigerant that has flowed out of the high-pressure side electric expansion valve 19a flows into the upstream branch portion 22, flows into the nozzle portion 13a side of the ejector 13, and the refrigerant suction port 13b side of the ejector 13 toward the fixed throttle 18 side. To the refrigerant flow flowing into the

  Here, in this embodiment, the flow rate ratio Ge / Gnoz between the refrigerant flow rate Gnoz flowing into the nozzle portion 13a side and the refrigerant flow rate Ge flowing into the refrigerant suction port 13b side is an optimum flow rate ratio that can exhibit a high COP as a whole cycle. The flow rate characteristics (pressure loss characteristics) of the nozzle portion 13 a and the fixed throttle 18, the refrigerant passage area in the upstream branch portion 22, and the like are determined.

The intermediate-pressure refrigerant that has flowed out from the upstream branching portion 22 toward the nozzle portion 13a is decompressed and expanded in an isentropic manner at the nozzle portion 13a and is injected (b ′ ₇ point → c ₇ point). As in the first embodiment, the refrigerant discharged from the second compressor 21 is sucked from the refrigerant suction port 13b by the refrigerant suction action of the injected refrigerant, and the injected refrigerant and the sucked refrigerant are mixed in the mixing unit 13c (c ₇ points → d ₇ points, j ₇ points → d ₇ points).

Mixed refrigerant is boosted by the diffuser part 13d (d ₇ points → e ₇ points), and flows into the outflow-side heat exchanger 52. Refrigerant flowing into the outflow-side heat exchanger 52, to be evaporated from the second storage-compartment air which is circulated blown by the blower fan 52a (e ₇ points → f ₇ points). Thereby, the air in the second storage is cooled. Refrigerant flowing out from the outflow-side heat exchanger 52 is sucked into the first compressor 11 again is compressed (f ₇ points → a _7-point).

On the other hand, the intermediate-pressure refrigerant that has flowed out from the upstream branching portion 22 toward the fixed throttle 18 is further decompressed and expanded isoenthalpically in the fixed throttle 18 to reduce its pressure (b ′ ₇ point → h ₇ point). ). Decompressed and expanded refrigerant at a fixed throttle 18 flows into the use-side heat exchanger 51, the blower fan 51a by such refrigerant is evaporated by absorbing heat from the first storage-compartment air circulating blower (h ₇ points → i ₇ points ). Thereby, the air in the first storage is cooled.

The refrigerant that has flowed out of the use-side heat exchanger 51 is sucked into the second compressor 21 through the second electric four-way valve 32 and compressed (i ₇ point → j ₇ point). Further, the refrigerant discharged from the second compressor 21 is sucked into the ejector 13 from the refrigerant suction port 13b (j ₇ point → d ₇ point). Other operations are the same as those in the first embodiment.

  Next, in the heating operation mode, the control device operates the first electric motor 11b and the blower fans 41a, 51a, and 52a, and switches the first and second electric four-way valves 31 and 32 to circuits indicated by broken line arrows, While the high pressure side electric expansion valve 19a is in the throttle state, the second electric motor 21b is stopped.

  Thereby, as shown by the broken line arrow in FIG. 6, the first compressor 11 (→ the first electric four-way valve 31 → the ejector 13 → the second electric four-way valve 32) → the use side heat exchanger 51 → the fixed throttle 18. (→ Upstream branch section 22) → High pressure side electric expansion valve 19a → Outdoor heat exchanger 41 (→ First electric type four-way valve 31) → Outflow side heat exchanger 52 → First compressor 11 in order of circulation A cycle is configured.

Therefore, the refrigerant compressed by the first compressor 11 (k ₇ points in FIG. 7 (b)), similarly to the first embodiment, is slightly reduced in pressure during flow back through the ejector 13 (k ₇ points → m ₇ point), and flows into the use side heat exchanger 51 via the second electric four-way valve 32.

Refrigerant flowing into the utilization-side heat exchanger 51, condensed by dissipating heat to air inside the heat exchanger, which is circulated blown from the blower fan 51a (m ₇ points → n ₇ points). Thereby, the air in the first storage is heated. The refrigerant radiated by the use side heat exchanger 51 flows into the fixed throttle 18 and is decompressed and expanded in an enthalpy manner (n ₇ points → n ′ ₇ points). The refrigerant decompressed and expanded by the fixed throttle 18 flows into the high-pressure side electric expansion valve 19a through the upstream branching portion 22.

  At this time, among the refrigerant pressures acting on the valve body portion of the second check valve 16b, the refrigerant pressure on the upstream branching portion 22 side is lower than the refrigerant pressure on the nozzle portion 13a side, so the second check valve 16b will be in a valve closing state. Accordingly, the refrigerant that has flowed into the upstream branch portion 22 does not flow out toward the nozzle portion 13a, but flows out of the refrigerant toward the high-pressure side electric expansion valve 19a.

The refrigerant that has flowed into the high-pressure side electric expansion valve 19 a is further decompressed and expanded in an isenthalpy manner (n ′ ₇ point → o ₇ point) and flows into the outdoor heat exchanger 41. At this time, the valve opening degree of the high-pressure side electric expansion valve 19a, the first compressor 11 the degree of superheat of the refrigerant on the suction side (p ₇ points) is adjusted to be predetermined value.

The refrigerant that has flowed into the outdoor heat exchanger 41 flows into the outdoor heat exchanger 41, and absorbs heat from outside air (outside air) blown by the blower fan 41a (from o ₇ point to o ′ ₇ point). The refrigerant that has flowed out of the outdoor heat exchanger 41 flows into the outflow side heat exchanger 52 via the first electric four-way valve 31, and further absorbs heat from the air in the second storage chamber that is circulated and blown by the blower fan 52a. And evaporate (o ' ₇ point-> p ₇ point).

Thereby, the air in the second storage is cooled. The refrigerant flowing out of the outflow side heat exchanger 52 is sucked into the first compressor 11 and compressed (p ₇ point → k ₇ point). Other operations are the same as those in the cooling operation mode.

  Therefore, when the ejector refrigeration cycle 200 of this embodiment is operated, in the cooling operation mode, the outdoor heat exchanger 41 functions as a radiator, and the use side heat exchanger 51 and the outflow side heat exchanger 52 serve as an evaporator. A functioning ejector refrigeration cycle is configured. Thereby, the air in the first storage can be cooled by the use side heat exchanger 51, and the air in the second storage can be cooled by the outflow side heat exchanger 52.

  At this time, the refrigerant evaporation pressure of the outflow side heat exchanger 52 becomes the pressure after being increased by the second compressor 21 and the diffuser unit 13d, while the refrigerant evaporation pressure of the use side heat exchanger 51 is the pressure at the fixed throttle 18. It becomes the pressure immediately after decompression.

  Therefore, the refrigerant evaporation pressure (refrigerant evaporation temperature) of the use side heat exchanger 51 can be made sufficiently lower than the refrigerant evaporation pressure (refrigerant evaporation temperature) of the outflow side heat exchanger 52. As a result, during the cooling operation mode, for example, the second storage is used as a refrigerator having an internal temperature of about 0 ° C. to 10 ° C., and the first storage is used with an internal temperature of about −30 ° C. to −10 ° C. It can be used as a freezer that cools to a low temperature.

  Further, in the heating operation mode, the refrigerant discharged from the first compressor 11 is radiated by the use side heat exchanger 51, and the radiated refrigerant is decompressed and expanded by the fixed throttle 18 and the high pressure side electric expansion valve 19a, and is decompressed and expanded. A refrigeration cycle is formed in which the refrigerant is evaporated by the outdoor heat exchanger 41 and the outflow side heat exchanger 52 and the evaporated refrigerant is pressurized again by the first compressor 11.

  Thereby, the air in the first storage can be heated by the use side heat exchanger 51, and the air in the second storage can be cooled by the outflow side heat exchanger 52. Further, in the ejector refrigeration cycle 200 of the present embodiment, not only the same effects as (A) to (D) of the first embodiment can be obtained, but also the following excellent effects can be obtained.

(F) During the cooling operation mode, the refrigerant (point b ′ _{7 in} FIG. 7A) decompressed and expanded by the high-pressure side electric expansion valve 19a is in a gas-liquid two-phase state, so the nozzle portion 13a of the ejector 13 The gas-liquid two-phase refrigerant can be introduced into the gas. Therefore, the boiling of the refrigerant in the nozzle portion 13a can be promoted and the nozzle efficiency can be improved as compared with the case where the liquid phase refrigerant is caused to flow into the nozzle portion 13a.

  As a result, the amount of recovered energy can be increased and the amount of pressure increase in the diffuser portion 13d can be increased, so that the COP can be further improved. Furthermore, since the refrigerant passage area of the nozzle portion 13a can be expanded as compared with the case where the liquid phase refrigerant is caused to flow into the nozzle portion 13a, the processing of the nozzle portion 13a is also facilitated. As a result, the manufacturing cost of the ejector 13 can be reduced, and the manufacturing cost of the ejector refrigeration cycle 200 as a whole can be reduced.

  (G) In the cooling operation mode, since the refrigerant flow is diverted so that the flow rate ratio Ge / Gnoz becomes the optimum flow rate ratio in the upstream branching section 22, the outflow side heat exchanger 52 functioning as an evaporator and The cycle can be operated while supplying a high flow rate refrigerant to both the use side heat exchangers 51 and exhibiting a high COP.

  (H) During the cooling operation mode, the refrigerant flow passing through the use side heat exchanger 51 and the outflow side heat exchanger 52 functioning as an evaporator becomes an annular shape having the first compressor 11 as a starting point and an end point, Even if oil (refrigeration machine oil) for lubricating the first and second compressors 11 and 21 is mixed into the refrigerant, the oil is contained in the outdoor heat exchanger 41, the use side heat exchanger 51, and the outflow side heat exchanger 52. Can be avoided.

(Fifth embodiment)
In the present embodiment, the ejector-type refrigeration is changed to a cold storage box in which the arrangement of the outflow side heat exchanger 52 is changed and the cold storage can be switched in both the first and second storage boxes as compared with the fourth embodiment. An example in which the cycle 200 is applied will be described. Specifically, as shown in the overall configuration diagram of FIG. 8, the outflow side heat exchanger 52 of the present embodiment includes the diffuser portion 13 d outlet of the ejector 13 and one refrigerant inlet and outlet of the first electric four-way valve 31. It is arranged between.

  Therefore, the first electric four-way valve 31 of the present embodiment is provided between the discharge side of the first compressor 11 and the outdoor heat exchanger 41 and between the outflow side heat exchanger 52 and the suction side of the first compressor 11. Between the refrigerant flow path (circuit indicated by the solid line arrow in FIG. 8), the discharge side of the first compressor 11 and the outflow side heat exchanger 52, and the outdoor heat exchanger 41 and the first compressor 11. The refrigerant flow path (circuit indicated by a broken line arrow in FIG. 8) that connects the suction port side at the same time is switched. Other configurations are the same as those of the fourth embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. 9A is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 9B is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a, 51a, and 52a, and the first and second electric four-way valves 31 and 32 are operated. The circuit is switched to the circuit indicated by the solid arrow, and the high pressure side electric expansion valve 19a is in the throttle state.

  Thereby, as shown by the solid line arrow in FIG. 8, the first compressor 11 (→ the first electric four-way valve 31) → the outdoor heat exchanger 41 → the high-pressure side electric expansion valve 19 a → the upstream branch portion 22 (→ The refrigerant circulates in the order of the second check valve 16 b) → the nozzle portion 13 a of the ejector 13 → the outflow side heat exchanger 52 (→ the first electric four-way valve 31) → the first compressor 11, and the upstream branch portion 22. → Fixed throttle 18 → Use-side heat exchanger 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → Refrigerant suction port 13b of the ejector 13 → outflow side heat exchange A cycle in which the refrigerant circulates is configured in the order of the unit 52 (→ first electric four-way valve 31) → first compressor 11.

  That is, in the cooling operation mode of the present embodiment, a cycle that is exactly the same as that of the cooling operation mode of the fourth embodiment is configured, and operates as shown in the Mollier diagram of FIG. The operation in the cooling operation mode is the same as the operation in the cooling operation mode of the fourth embodiment (FIG. 7A). Therefore, in the cooling operation mode of the present embodiment, the same effect as that of the cooling operation mode of the fourth embodiment can be obtained.

  Next, in the heating operation mode, the control device operates the first electric motor 11b and the blower fans 41a, 51a, and 52a, and switches the first and second electric four-way valves 31 and 32 to circuits indicated by broken line arrows, While the high pressure side electric expansion valve 19a is in the throttle state, the second electric motor 21b is stopped.

  Thereby, as shown by the broken line arrow in FIG. 8, the first compressor 11 (→ the first electric four-way valve 31) → the outflow side heat exchanger 52 (→ the ejector 13 → the second electric four-way valve 32) → use Refrigerant circulates in the order of side heat exchanger 51 → fixed throttle 18 → upstream branch portion 22 → high pressure side electric expansion valve 19a → outdoor heat exchanger 41 (→ first electric four-way valve 31) → first compressor 11 A cycle is configured.

Therefore, the refrigerant compressed by the first compressor 11 (k ₉ points in FIG. 9 (b)) flows into the outlet-side heat exchanger 52 via the first electric four-way valve 31, the blower fan 52a The heat is exchanged with the air in the second storage chamber that is circulated and radiated (k ₉ points → k ′ ₉ points). Thereby, the air in the second storage is heated.

The refrigerant that has radiated heat in the outflow side heat exchanger 52 is slightly decompressed (k ′ ₉ point → m ₉ point) when flowing backward in the ejector 13, and the use side heat is passed through the second electric four-way valve 32. It flows into the exchanger 51. Refrigerant flowing into the utilization-side heat exchanger 51, the blower fan 51a within the first exchanging heat with air storage chamber that is circulated blown by the heat dissipation to condense (m ₉ points → n ₉ points). Thereby, the air in the first storage is heated.

As in the fourth embodiment, the refrigerant flowing out from the use side heat exchanger 51 is decompressed and expanded in an enthalpy manner in the order of the fixed throttle 18 → the high pressure side electric expansion valve 19a (n ₉ points → n ′ ₉ points). → o ₉ points), flows into the outdoor heat exchanger 41. The refrigerant flowing into the outdoor heat exchanger 41 absorbs heat from the outside air blown from the blower fan 41a (o ₉ point → p ₉ point). The refrigerant flowing out of the outdoor heat exchanger 41 is sucked into the first compressor 11 through the first electric four-way valve 31 and compressed again.

  Other operations are the same as those in the heating operation mode of the fourth embodiment. Therefore, in the heating operation mode of the present embodiment, the refrigerant discharged from the first compressor 11 is radiated by the outflow side heat exchanger 52 and the use side heat exchanger 51, and the radiated refrigerant is discharged by the fixed throttle 18 and the high pressure side electric expansion. A refrigerating cycle is configured in which the decompressed and expanded refrigerant is evaporated by the valve 19a, the decompressed and expanded refrigerant is evaporated by the outdoor heat exchanger 41, and the evaporated refrigerant is increased again by the first compressor 11.

  Thereby, the air in the first storage can be heated by the use side heat exchanger 51, and the air in the second storage can be heated by the outflow side heat exchanger 52. Furthermore, the same effects as (C) and (D) of the first embodiment can be obtained.

(Sixth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 10, the connection mode of each component device is changed with respect to the ejector refrigeration cycle 200 of the fourth embodiment, and the second compressor 21 is changed in the heating operation mode. An example in which the cycle is switched to a cycle in which the refrigerant is compressed and discharged by the (second compression mechanism 21a) will be described.

  Specifically, the outflow side heat exchanger 52 of the present embodiment is provided between the outlet of the diffuser portion 13d of the ejector 13 and one refrigerant inflow / outlet of the first electric four-way valve 31, as in the fifth embodiment. Has been placed.

  The first electric four-way valve 31 simultaneously connects the first compressor 11 outlet side and the outdoor heat exchanger 41 and the outflow side heat exchanger 52 and the first compressor 11 suction side. The refrigerant flow path (the circuit indicated by the solid line arrow in FIG. 10), the outdoor heat exchanger 41 and the outflow side heat exchanger 52, and the first compressor 11 discharge port side and suction port side are simultaneously connected. The refrigerant flow path (the circuit indicated by the broken line arrow in FIG. 10) is switched.

  Further, the second electric four-way valve 32 is provided between the use-side heat exchanger 51 and the second compressor 21 suction port side and between the second compressor 21 discharge port side and the refrigerant suction port 13b side of the ejector 13 simultaneously. The refrigerant flow path (circuit shown by the solid line arrow in FIG. 10) to be connected, between the second compressor 21 discharge port side and the use side heat exchanger 51, the refrigerant suction port 13b side, and the second compressor 21 suction port side. Are switched to the refrigerant flow paths (circuits indicated by broken line arrows in FIG. 10) that are simultaneously connected to each other. Other configurations are the same as those of the fourth embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 11A is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 11B is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a, 51a, and 52a, and the first and second electric four-way valves 31 and 32 are operated. The circuit is switched to the circuit indicated by the solid arrow, and the high pressure side electric expansion valve 19a is in the throttle state.

  Thereby, as shown by the solid line arrow in FIG. 10, the first compressor 11 (→ the first electric four-way valve 31) → the outdoor heat exchanger 41 → the high-pressure side electric expansion valve 19a → the upstream branch portion 22 (→ The refrigerant circulates in the order of the second check valve 16 b) → the nozzle portion 13 a of the ejector 13 → the outflow side heat exchanger 52 (→ the first electric four-way valve 31) → the first compressor 11, and the upstream branch portion 22. → Fixed throttle 18 → Use-side heat exchanger 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → Refrigerant suction port 13b of the ejector 13 → outflow side heat exchange A cycle in which the refrigerant circulates is configured in the order of the unit 52 (→ first electric four-way valve 31) → first compressor 11.

  That is, in the cooling operation mode of the present embodiment, a cycle exactly the same as the cooling operation mode of the fourth embodiment is configured, and operates as shown in the Mollier diagram of FIG. The operation in the cooling operation mode is the same as the operation in the cooling operation mode of the fourth embodiment (FIG. 7A). Therefore, in the cooling operation mode of the present embodiment, the same effect as that of the cooling operation mode of the fourth embodiment can be obtained.

  Next, in the heating operation mode, the control device operates the second electric motor 21b and the blower fans 41a, 51a, and 52a, and switches the first and second electric four-way valves 31 and 32 to circuits indicated by broken line arrows, The high pressure side electric expansion valve 19a is brought into a throttled state, and the first electric motor 11b is stopped.

  As a result, as shown by the broken line arrow in FIG. 10, the second compressor 21 (→ second electric four-way valve 32) → the use side heat exchanger 51 → the fixed throttle 18 → the upstream branching section 22 → the high pressure side electric type. The refrigerant circulates in the following order: expansion valve 19a → outdoor heat exchanger 41 (→ first electric four-way valve 31) → outflow side heat exchanger 52 (→ ejector 13 → second electric four-way valve 32) → second compressor 21. A cycle is configured.

Accordingly, the refrigerant (the l ₁₁ point in FIG. 11B) compressed by the second compressor 21 flows into the use-side heat exchanger 51 via the second electric four-way valve 32 and is blown by the blower fan 51a. Heat is exchanged with the circulating air in the first storage chamber to dissipate heat (l ₁₁ points → n ₁₁ points). Thereby, the air in the first storage is heated.

As in the fourth embodiment, the refrigerant flowing out from the use side heat exchanger 51 is decompressed and expanded in an enthalpy manner in the order of the fixed throttle 18 → the high pressure side electric expansion valve 19a (n ₁₁ points → n ′ ₁₁ points). → o ₁₁ points), flows into the outdoor heat exchanger 41. Refrigerant flowing into the outdoor heat exchanger 41 absorbs heat from outside air blown from the blower fan 41a (o ₁₁ points → o _'11 points).

The refrigerant that has flowed out of the outdoor heat exchanger 41 flows into the outflow side heat exchanger 52 through the first electric four-way valve 31, and absorbs heat from the air in the second storage chamber that is circulated and blown by the blower fan 52a. evaporation (o _'11-point → p ₁₁ points). Thereby, the air in the second storage is cooled.

Refrigerant flowing out from the outflow-side heat exchanger 52 flows into the ejector 13 through the first electric four-way valve 31, it is slightly reduced in pressure when reverse flow through the ejector 13 (p ₁₁ points → m ₁₁ points ). Further, the air is sucked into the second compressor 21 through the second electric four-way valve 32 and compressed again. Other operations are the same as those in the fourth embodiment.

  Therefore, in the heating operation mode of the present embodiment, the refrigerant discharged from the second compressor 21 is radiated by the use side heat exchanger 51, and the radiated refrigerant is decompressed and expanded by the fixed throttle 18 and the high pressure side electric expansion valve 19a. Then, a refrigerant cycle in which the refrigerant expanded under reduced pressure is evaporated in the outdoor heat exchanger 41 and the outflow side heat exchanger 52 and the evaporated refrigerant is pressurized again in the second compressor 21 is configured.

  That is, in the heating operation mode of the present embodiment, the second compressor 21 fulfills the function of the first compressor 11 in the fourth embodiment, so that the cycle is substantially the same as in the heating operation mode of the fourth embodiment. Can be configured. As a result, the air in the first storage can be heated by the use side heat exchanger 51, and the air in the second storage can be cooled by the outflow side heat exchanger 52, which is the same as the heating operation mode of the fourth embodiment. The effect of can be obtained.

(Seventh embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 12, the connection mode of each component device is changed with respect to the ejector refrigeration cycle 200 of the fourth embodiment, and the second compressor 21 is changed in the heating operation mode. The cycle is switched to a cycle in which the refrigerant is compressed and discharged by the (second compression mechanism 21a). In the ejector refrigeration cycle 200 of the present embodiment, the air in the second storage compartment is neither heated nor cooled during the heating operation mode.

  Specifically, the outflow side heat exchanger 52 of the present embodiment is disposed between one refrigerant inflow / outlet of the first electric four-way valve 31 and the suction port of the first compressor 11.

  The first electric four-way valve 31 simultaneously connects the discharge side of the first compressor 11 and the outdoor heat exchanger 41 and the outlet side of the diffuser section of the ejector 13 and the outflow side heat exchanger 52. Between the refrigerant flow path (circuit shown by the solid line arrow in FIG. 12), the outdoor heat exchanger 41 and the diffuser portion outlet side of the ejector 13, and between the outflow side heat exchanger 52 and the first compressor 11 inlet side. Are switched to the refrigerant flow paths (circuits indicated by broken line arrows in FIG. 12).

  Further, the second electric four-way valve 32 is provided between the use-side heat exchanger 51 and the second compressor 21 suction port side and between the second compressor 21 discharge port side and the refrigerant suction port 13b side of the ejector 13 simultaneously. The refrigerant flow path (circuit shown by the solid line arrow in FIG. 12) to be connected, between the second compressor 21 discharge port side and the use side heat exchanger 51, the refrigerant suction port 13b side, and the second compressor 21 suction port side. Are switched to the refrigerant flow paths (circuits indicated by broken line arrows in FIG. 12) that are simultaneously connected to each other. Other configurations are the same as those of the fourth embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 13A is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 13B is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a, 51a, and 52a, and the first and second electric four-way valves 31 and 32 are operated. The circuit is switched to the circuit indicated by the solid arrow, and the high pressure side electric expansion valve 19a is in the throttle state.

  Thereby, as shown by the solid line arrow in FIG. 12, the first compressor 11 (→ the first electric four-way valve 31) → the outdoor heat exchanger 41 → the high-pressure side electric expansion valve 19 a → the upstream branch portion 22 (→ The refrigerant circulates in the order of the second check valve 16b) → the nozzle part 13a of the ejector 13 (→ the first electric four-way valve 31) → the outflow side heat exchanger 52 → the first compressor 11, and the upstream side branch part 22 → Fixed throttle 18 → Use side heat exchanger 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → refrigerant suction port 13b of the ejector 13 (→ first electric A cycle in which the refrigerant circulates in the order of the four-way valve 31) → the outflow side heat exchanger 52 → the first compressor 11.

  That is, in the cooling operation mode of the present embodiment, a cycle exactly the same as the cooling operation mode of the fourth embodiment is configured, and operates as shown in the Mollier diagram of FIG. The operation in the cooling operation mode is the same as the operation in the cooling operation mode of the fourth embodiment (FIG. 7A). Therefore, in the cooling operation mode of the present embodiment, the same effect as that of the cooling operation mode of the fourth embodiment can be obtained.

  Next, in the heating operation mode, the control device operates the second electric motor 21b and the blower fans 41a and 51a to switch the first and second electric four-way valves 31 and 32 to the circuit indicated by the broken-line arrow, While the electric expansion valve 19a is in the throttle state, the first electric motor 11b and the blower fan 52a are stopped.

  Thereby, as shown by the broken line arrow in FIG. 12, the second compressor 21 (→ second electric four-way valve 32) → the use side heat exchanger 51 → the fixed throttle 18 → the upstream branching section 22 → the high pressure side electric type. A cycle in which the refrigerant circulates is configured in the order of the expansion valve 19a → the outdoor heat exchanger 41 (→ first electric four-way valve 31 → ejector 13 → second electric four-way valve 32) → second compressor 21.

Accordingly, the refrigerant (the point l _{13 in} FIG. 13B) compressed by the second compressor 21 flows into the use side heat exchanger 51 through the second electric four-way valve 32 and is blown by the blower fan 51a. Heat is exchanged with the circulating air in the first storage chamber to dissipate heat (l ₁₃ points → n ₁₃ points). Thereby, the air in the first storage is heated.

As in the fourth embodiment, the refrigerant flowing out from the use side heat exchanger 51 is decompressed and expanded in an enthalpy manner in the order of the fixed throttle 18 → the high pressure side electric expansion valve 19a (n ₁₃ points → n ′ ₁₃ points). → o ₁₃ points), flows into the outdoor heat exchanger 41. Refrigerant flowing into the outdoor heat exchanger 41 absorbs heat from outside air blown from the blower fan 41a (o ₁₃ points → p ₁₃ points).

The refrigerant flowing out from the outdoor heat exchanger 41 flows into the ejector 13 through the first electric four-way valve 31, is slightly reduced in pressure during flow back through the ejector 13 (p ₁₃ points → m ₁₃ points) Then, it is sucked into the second compressor 21 via the second electric four-way valve 32 and compressed again. Other operations are the same as those in the fourth embodiment.

  Therefore, in the heating operation mode of the present embodiment, the refrigerant discharged from the second compressor 21 is radiated by the use side heat exchanger 51, and the radiated refrigerant is decompressed and expanded by the fixed throttle 18 and the high pressure side electric expansion valve 19a. Thus, a refrigerant cycle in which the decompressed and expanded refrigerant is evaporated in the outdoor heat exchanger 41 and the evaporated refrigerant is increased in pressure by the second compressor 21 is configured.

  Thereby, in the heating operation mode of the present embodiment, the second compressor 21 fulfills the function of the first compressor 11 in the fourth embodiment, although the air in the second storage compartment cannot be cooled or heated. Thus, the use-side heat exchanger 51 can heat the air in the first storage.

(Eighth embodiment)
14 and 15, an example in which the ejector refrigeration cycle 300 of the present invention is applied to the same cold storage as in the first embodiment will be described. FIG. 14 is an overall configuration diagram of the ejector refrigeration cycle 300 of the present embodiment. The ejector refrigeration cycle 300 is obtained by changing the cycle configuration with respect to the ejector refrigeration cycle 200 of the fourth embodiment, which is the premise thereof.

  As shown in FIG. 14, in the ejector refrigeration cycle 300 of this embodiment, the outflow side heat exchanger 52 is abolished and an internal heat exchanger 35 is added to the ejector refrigeration cycle 200 of the fourth embodiment. is doing.

  In the cooling operation mode, the internal heat exchanger 35 is branched by the upstream branching portion 22 that passes through the high-pressure refrigerant passage 35a and flows out to the fixed throttle 18 side, and passes through the low-pressure refrigerant passage 35b. Heat exchange is performed with the refrigerant sucked by the second compressor 21.

  As a specific configuration of the internal heat exchanger 35, a double-pipe heat exchanger configuration in which an inner tube that forms a low-pressure refrigerant passage 35b is disposed inside an outer tube that forms a high-pressure refrigerant channel 35a. Is adopted. Of course, the high-pressure side refrigerant flow path 35a may be an inner pipe and the low-pressure side refrigerant flow path 35b may be an outer pipe. Further, a configuration in which the refrigerant pipes forming the high-pressure side refrigerant flow path 35a and the low-pressure side refrigerant flow path 35b are brazed and joined to exchange heat may be employed.

  In the present embodiment, as described above, the outflow side heat exchanger 52 is abolished and the internal heat exchanger 35 is added. For this reason, the first electric four-way valve 31 is provided between the discharge side of the first compressor 11 and the outdoor heat exchanger 41 and between the outlet side of the diffuser portion 13d of the ejector 13 and the suction side of the first compressor 11. Between the refrigerant flow path (circuit indicated by the solid line arrow in FIG. 14), the discharge side of the first compressor 11 and the outlet side of the diffuser portion 13d of the ejector 13, and the outdoor heat exchanger 41 and the first compressor 11 is switched to a refrigerant flow path (circuit indicated by a broken line arrow in FIG. 14) that is simultaneously connected to the suction port side.

  Further, the second electric four-way valve 32 is provided between the low-pressure side refrigerant flow path 35b of the internal heat exchanger 35 and the second compressor 21 suction port side, and between the second compressor 21 discharge port side and the refrigerant suction of the ejector 13. The refrigerant flow path (circuit indicated by the solid line arrow in FIG. 14) that connects the side of the port 13b at the same time, the refrigerant suction port 13b side, the low-pressure side refrigerant flow path 35b of the internal heat exchanger 35, and the second compressor 21 The refrigerant flow path (circuit indicated by a broken line arrow in FIG. 14) that connects the suction port side and the discharge port side at the same time is switched.

  Furthermore, in the present embodiment, a high-pressure side electric expansion valve 19a similar to that of the fourth embodiment is disposed between the upstream branching portion 22 and the nozzle portion 13a inlet side of the ejector 13.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 15A is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 15B is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a and 51a to bring the high-pressure side electric expansion valve 19a into a throttle state, 1. Switch the second electric four-way valves 31, 32 to a circuit indicated by solid arrows.

  Thereby, as shown by the solid line arrow in FIG. 14, the first compressor 11 (→ the first electric four-way valve 31) → the outdoor heat exchanger 41 → the upstream branch portion 22 → the high pressure side electric expansion valve 19 a → the ejector The refrigerant circulates in the order of 13 nozzle parts 13a (→ first electric four-way valve 31) → first compressor 11, and upstream side branch part 22 → high pressure side refrigerant flow path 35a of the internal heat exchanger 35 → fixed throttle. 18 → use side heat exchanger 51 → low pressure side refrigerant flow path 35b of internal heat exchanger 35 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → ejector 13 The refrigerant circulation port 13b (→ the first electric four-way valve 31) → the first compressor 11 is cycled in this order.

Therefore, the refrigerant compressed by the first compressor 11 (a ₁₅ in FIG. 15 (a)), similarly to the fourth embodiment, outside-compartment air blown from the blower fan 41a in the outdoor heat exchanger 41 Heat exchanges with (outside air) to dissipate heat and condense (a ₁₅ points → b ₁₅ points). The refrigerant that has flowed out of the outdoor heat exchanger 41 flows into the upstream branch portion 22 and flows into the high-pressure side electric expansion valve 19a side and into the high-pressure side refrigerant flow path 35a side of the internal heat exchanger 35. The refrigerant flow is divided.

The refrigerant that has flowed from the upstream branching portion 22 to the high pressure side electric expansion valve 19a side is decompressed and expanded in an enthalpy manner at the high pressure side electric expansion valve 19a to become a gas-liquid two-phase intermediate pressure refrigerant (b). ₁₅ points → b _'15 points). At this time, the valve opening degree of the high-pressure side electric expansion valve 19a is degree of superheat of the refrigerant in the first compressor 11 inlet side ₍₁₅ points f) is adjusted to be predetermined value.

The intermediate-pressure refrigerant flowing out from the high-pressure side electric expansion valve 19a, as in the fourth embodiment, is injected under reduced pressure expands isentropically to at the nozzle portion 13a of the ejector 13 (b _'15-point → c ₁₅ points ) And mixed with the refrigerant discharged from the second compressor 21 (c ₁₅ point → d ₁₅ point, j ₁₅ point → d ₁₅ point), and the pressure is increased by the diffuser portion 13d (d ₁₅ point → e ₁₅ point).

The refrigerant flowing out of the diffuser section 13d absorbs heat from ambient air or the like through the refrigerant pipe leading to the first compressor 11 suction port, increases the enthalpy (e ₁₅ point → f ₁₅ point), and is sucked into the first compressor 11 And compressed (f ₁₅ points → a ₁₅ points).

On the other hand, the high-pressure refrigerant that has flowed into the high-pressure side refrigerant flow path 35a of the internal heat exchanger 35 from the upstream branching portion 22 exchanges heat with the second compressor 21 suction refrigerant flowing through the low-pressure side refrigerant flow path 35b, and The enthalpy is reduced (b ₁₅ points → b ″ ₁₅ points). Along with this, the enthalpy of the refrigerant sucked in the second compressor 21 increases (i ₁₅ points → i ′ ₁₅ points).

The refrigerant that has flowed out of the high-pressure side refrigerant flow path 35a of the internal heat exchanger 35 is further decompressed and expanded in an isenthalpy manner by the fixed restrictor 18 to reduce its pressure (b ″ ₁₅ points → h ₁₅ points). Subsequent operations are the same as those in the fourth embodiment.

  Next, in the heating operation mode, the control device operates the first electric motor 11b and the blower fans 41a and 51a to switch the first and second electric four-way valves 31 and 32 to a circuit indicated by a broken-line arrow, The electric expansion valve 19a is fully closed and the second electric motor 21b is stopped.

  Accordingly, as indicated by the broken line arrow in FIG. 14, the first compressor 11 (→ the first electric four-way valve 31 → the ejector 13 → the second electric four-way valve 32) → the low-pressure side refrigerant flow of the internal heat exchanger 35 Path 35b → use side heat exchanger 51 → fixed throttle 18 → high pressure side refrigerant flow path 35a of the internal heat exchanger 35 → upstream branch portion 22 → outdoor heat exchanger 41 (→ first electric four-way valve 31) → first A cycle in which the refrigerant circulates in the order of the one compressor 11 is configured.

Therefore, the refrigerant compressed by the first compressor 11 (k ₁₅ points in FIG. 11 (b)) is just in the same manner as in the fourth embodiment, flows into the ejector 13 flows back through the ejector 13 (K ₁₅ point → m ₁₅ point) and flows into the low-pressure side refrigerant flow path 35 b of the internal heat exchanger 35 through the second electric four-way valve 32.

Then, the refrigerant flowing into the low-pressure side refrigerant flow path 35b of the internal heat exchanger 35 exchanges heat with the refrigerant flowing out of the fixed throttle 18 flowing through the high-pressure side refrigerant flow path 35a to further reduce the enthalpy (m ₁₅ points). → m _'15 points). Along with this, the enthalpy of the refrigerant flowing out of the fixed throttle 18 increases (o ₁₅ points → o ′ ₁₅ points).

The refrigerant that has flowed out of the low-pressure side refrigerant flow path 35b of the internal heat exchanger 35 flows into the use-side heat exchanger 51 and exchanges heat with the internal air circulated and blown from the blower fan 51a to radiate heat (m ′ ₁₅ Point → n ₁₅ points). As a result, the internal air is heated. The refrigerant that has flowed out of the use-side heat exchanger 51 is decompressed and expanded by the fixed throttle 18 (n ₁₅ point → o ₁₅ point), and passes through the high-pressure side refrigerant flow path 35 a and the upstream branching portion 22 of the internal heat exchanger 35. And flows into the outdoor heat exchanger 41.

Here, the refrigerant flowing out from the high-pressure side refrigerant flow path 35a of the internal heat exchanger 35 has the high-pressure side electric expansion valve 19a fully closed, so that the entire flow rate thereof flows into the outdoor heat exchanger 41. Then, heat is exchanged with the outside air blown from the blower fan 41a to absorb heat (o ′ ₁₅ points → p ₁₅ points). The refrigerant that has flowed out of the outdoor heat exchanger 41 is sucked into the first compressor 11 and compressed (p ₁₅ points → k ₁₅ points). Other operations are the same as those in the fourth embodiment.

  Therefore, when the ejector refrigeration cycle 300 of this embodiment is operated, in the cooling operation mode, an ejector refrigeration cycle in which the outdoor heat exchanger 41 functions as a radiator and the use side heat exchanger 51 functions as an evaporator is provided. Composed. Thereby, the inside air can be cooled by the use side heat exchanger 51.

  In the heating operation mode, the refrigerant discharged from the first compressor 11 is radiated by the use side heat exchanger 51, the radiated refrigerant is decompressed and expanded by the fixed throttle 18, and the decompressed and expanded refrigerant is circulated by the outdoor heat exchanger 41. A refrigeration cycle in which the evaporated refrigerant is increased in pressure by the first compressor 11 is configured. Thereby, the internal air can be heated by the use side heat exchanger 51.

  Further, in the ejector refrigeration cycle 300 of the present embodiment, the same effects as (A) to (D) of the first embodiment and the same effects as (F) and (H) of the fourth embodiment are obtained. The following excellent effects can also be obtained.

  (I) Refrigeration capacity by expanding the enthalpy difference between the enthalpy of the inlet side refrigerant and the enthalpy of the outlet side refrigerant of the use side heat exchanger 51 acting as an evaporator by the action of the internal heat exchanger 35 in the cooling operation mode Can be increased. Thereby, COP can be improved further.

  (J) During the cooling operation mode, the internal heat exchanger 35 heats the high-pressure refrigerant flowing through the refrigerant passage from the upstream branching portion 22 to the inlet of the fixed throttle 18 and the low-pressure refrigerant sucked into the second compression mechanism 21a. Since they are exchanged, the enthalpy of the refrigerant flowing from the upstream branching portion 22 into the nozzle portion 13a is not unnecessarily lowered.

  Thereby, the further COP improvement effect can be acquired. The reason is that the amount of recovered energy in the nozzle portion 13a can be increased by unnecessarily reducing the enthalpy of the refrigerant flowing into the nozzle portion 13a.

  This will be described in more detail. As the enthalpy of the refrigerant flowing into the nozzle portion 13a increases, the slope of the isentropic line becomes gentle. Therefore, in the case where the nozzle portion 13a is isentropically expanded by the same pressure, the higher the enthalpy of the nozzle portion 13a inlet-side refrigerant, the higher the enthalpy of the nozzle portion 13a inlet-side refrigerant and the enthalpy of the nozzle portion 13a outlet-side refrigerant. The difference (recovered energy amount) increases.

  Accordingly, as the enthalpy of the refrigerant flowing into the nozzle portion 13a increases, the amount of recovered energy in the nozzle portion 13a increases. As the amount of recovered energy increases, the amount of pressure increase in the diffuser portion 13d can be increased, and a further COP improvement effect can be obtained.

  Further, in the heating operation mode of the present embodiment, compared to the case where the internal heat exchanger 35 is not provided, the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 41 from the outside air and the refrigerant in the use side heat exchanger 52. Although the amount of heat radiation that can be radiated is slightly reduced, the cycle can be stably operated as in (c) of the first embodiment.

  Furthermore, a bypass passage through which the refrigerant flows so as to bypass at least one refrigerant flow path of the internal heat exchanger 35 may be added to the cycle of the present embodiment in the heating operation mode. Thereby, at the time of heating operation mode, the function of the internal heat exchanger 35 can be suppressed, and the reduction of the heat radiation amount of the refrigerant in the use side heat exchanger 52 can be suppressed.

(Ninth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 16, the connection mode of each component device is changed with respect to the ejector refrigeration cycle 300 of the eighth embodiment, and the second compressor 21 is in the heating operation mode. An example in which the cycle is switched to a cycle in which the refrigerant is compressed and discharged by the (second compression mechanism 21a) will be described.

  Specifically, the first electric four-way valve 31 of the present embodiment includes the first compressor 11 between the outlet side of the first compressor 11 and the outdoor heat exchanger 41, the outlet side of the diffuser portion 13 d of the ejector 13, and the first compressor 11. A refrigerant flow path (circuit indicated by a solid line arrow in FIG. 16) that connects the suction port side at the same time, between the outdoor heat exchanger 41 and the diffuser portion 13d outlet side of the ejector 13, and the discharge port of the first compressor 11 The refrigerant flow paths (circuits indicated by broken line arrows in FIG. 16) that simultaneously connect the suction side and the suction port side are switched.

  Further, the second electric four-way valve 32 is provided between the low-pressure side refrigerant flow path 35b of the internal heat exchanger 35 and the second compressor 21 suction port side, and between the second compressor 21 discharge port side and the refrigerant suction of the ejector 13. The refrigerant flow path (circuit indicated by the solid line arrow in FIG. 16) that connects the side of the port 13b at the same time, the discharge side of the second compressor 21 and the low-pressure side refrigerant flow path 35b of the internal heat exchanger 35, and the ejector 13 The refrigerant flow path (circuit indicated by a broken line arrow in FIG. 16) that simultaneously connects the refrigerant suction port 13b side and the second compressor 21 suction side is switched. Other configurations are the same as those of the fourth embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 17A is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 17B is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a and 51a, and the first and second electric four-way valves 31 and 32 are indicated by solid arrows. The high pressure side electric expansion valve 19a is in the throttle state.

  As a result, as indicated by the solid line arrow in FIG. 16, the first compressor 11 (→ first electric four-way valve 31) → outdoor heat exchanger 41 → upstream branch portion 22 → high pressure side electric expansion valve 19a → ejector The refrigerant circulates in the order of 13 nozzle parts 13a (→ first electric four-way valve 31) → first compressor 11, and upstream side branch part 22 → high pressure side refrigerant flow path 35a of the internal heat exchanger 35 → fixed throttle. 18 → use side heat exchanger 51 → low pressure side refrigerant flow path 35b of internal heat exchanger 35 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → ejector 13 The refrigerant circulation port 13b (→ the first electric four-way valve 31) → the first compressor 11 is cycled in this order.

  That is, in the cooling operation mode of the present embodiment, a cycle exactly the same as the cooling operation mode of the eighth embodiment is configured and operates as shown in the Mollier diagram of FIG. The operation in the cooling operation mode is the same as the operation in the cooling operation mode of the eighth embodiment (FIG. 15A). Therefore, in the cooling operation mode of the present embodiment, the same effect as that of the cooling operation mode of the eighth embodiment can be obtained.

  Next, in the heating operation mode, the second electric motor 21b and the blower fans 41a and 51a are operated, and the first and second electric four-way valves 31 and 32 are switched to the circuit indicated by the broken-line arrow, and the high-pressure side electric expansion valve While 19a is made into a fully closed state, the 1st electric motor 11b is stopped.

  As a result, as indicated by a broken line arrow in FIG. 16, the second compressor 21 (→ second electric four-way valve 32) → the low pressure side refrigerant flow path 35b of the internal heat exchanger 35 → the use side heat exchanger 51 → fixed. Restrictor 18 → High-pressure side refrigerant flow path 35a of internal heat exchanger 35 → upstream branch portion 22 → outdoor heat exchanger 41 (→ first electric four-way valve 31 → ejector 13 → second electric four-way valve 32) → second A cycle in which the refrigerant circulates in the order of the two compressors 21 is configured.

Therefore, the refrigerant compressed by the second compressor 21 (point l _{17 in} FIG. 17B) goes to the low-pressure side refrigerant flow path 35b of the internal heat exchanger 35 via the second electric four-way valve 32. Heat is exchanged with the refrigerant flowing out of the fixed throttle 18 flowing in and flowing through the high-pressure side refrigerant flow path 35a to further reduce the enthalpy (l ₁₇ points → l ′ ₁₇ points). Along with this, the enthalpy of the refrigerant flowing out of the fixed throttle 18 increases (from o ₁₇ point to o ′ ₁₇ point).

The refrigerant that has flowed out of the high-pressure side refrigerant flow path 35a of the internal heat exchanger 35 flows into the outdoor heat exchanger 41 and absorbs heat from the outside air blown from the blower fan 41a (o ₁₇ point → p ₁₇ point). The refrigerant flowing out from the outdoor heat exchanger 41 flows into the ejector 13 through the first electric four-way valve 31, is slightly reduced in pressure during flow back through the ejector 13 (p ₁₃ points → m ₁₃ points) Then, it is sucked into the second compressor 21 via the second electric four-way valve 32 and compressed again. Other operations are the same as those in the seventh embodiment.

  Therefore, in the heating operation mode of the present embodiment, the refrigerant discharged from the second compressor 21 is radiated by the use-side heat exchanger 51, the radiated refrigerant is decompressed and expanded by the fixed throttle 18, and the decompressed and expanded refrigerant is subjected to outdoor heat. A refrigeration cycle is configured in which the refrigerant is evaporated by the exchanger 41 and the evaporated refrigerant is again pressurized by the second compressor 21.

  That is, in the heating operation mode of the present embodiment, the second compressor 21 fulfills the function of the first compressor 11 in the eighth embodiment, so that the cycle is substantially the same as in the heating operation mode of the eighth embodiment. Can be configured. As a result, the inside air can be heated by the use side heat exchanger 51, and the same effect as the heating operation mode of the fourth embodiment can be obtained.

(10th Embodiment)
18 and 19, an example in which the ejector refrigeration cycle 400 of the present invention is applied to a cold storage having two storages that can be switched between cold storage as in the fifth embodiment will be described. FIG. 18 is an overall configuration diagram of the ejector refrigeration cycle 400 of the present embodiment. The ejector refrigeration cycle 400 is obtained by changing the cycle configuration with respect to the ejector refrigeration cycle 100 of the first embodiment, which is the premise thereof.

  As shown in FIG. 18, in the ejector type refrigeration cycle 400 of the present embodiment, the accumulator 14, the separated refrigerant fixed throttle 15, and the first check valve 16a are eliminated from the first embodiment. And the downstream branch part 23 which branches the flow of the refrigerant | coolant which flowed out from the diffuser part 13d is provided in the diffuser part 13d exit side of the ejector 13, and the outflow side heat exchanger 52 similar to 4th Embodiment is provided. .

  The basic configuration of the downstream branch portion 23 is the same as that of the upstream branch portion 22 of the fourth embodiment. An outflow side heat exchanger 52 is connected to one refrigerant outlet 23b of the downstream branching portion 23, and a low pressure side electric expansion valve 19b serving as a low pressure side decompression means is connected to the other refrigerant outlet 23c. Thus, one refrigerant inflow / outlet side of the first three-way joint 17a is connected.

  Further, the downstream branching section 23 flows in the direction of the refrigerant flowing out from the one refrigerant outlet 23b to the outflow side heat exchanger 52, and flows out from the other refrigerant outlet 23c to the low pressure side electric expansion valve 19b. The flow direction of the refrigerant is substantially Y-shaped so as to face the target direction and intersect at an acute angle with respect to the flow direction of the refrigerant flowing into the refrigerant inlet 23a from the diffuser portion 13d outlet side.

  Therefore, the refrigerant that has flowed into the downstream branch portion 23 flows out of the downstream branch portion 23 without unnecessarily reducing the flow velocity when the flow is branched. Thereby, the flow velocity (dynamic pressure) of the refrigerant that has flowed out of the ejector 13 at the downstream branch portion 23 is maintained. Of course, the downstream branching portion 23 is not limited to this, and may be formed in a substantially T-shape or the like.

  In addition, one refrigerant inlet / outlet of the first electric four-way valve 31 is connected to the other refrigerant inlet / outlet of the outflow side heat exchanger 52 of the present embodiment. The basic configuration of the low pressure side electric expansion valve 19b is the same as that of the high pressure side electric expansion valve 19a. Furthermore, the high pressure side electric expansion valve 19a of the present embodiment is disposed in the refrigerant passage from the electric three-way valve 33 to the inlet side of the nozzle portion 13a, and the degree of superheat of the refrigerant sucked in the first compressor 11 is preset. The valve opening is adjusted to a predetermined value.

  Therefore, the first electric four-way valve 31 of the present embodiment is provided between the discharge side of the first compressor 11 and the outdoor heat exchanger 41 and between the outflow side heat exchanger 52 and the suction side of the first compressor 11. The refrigerant flow path (circuit shown by the solid line arrow in FIG. 18) that connects them at the same time, between the discharge side of the first compressor 11 and the outflow side heat exchanger 52, and between the outdoor heat exchanger 41 and the first compressor 11. The refrigerant flow path (circuit indicated by a broken line arrow in FIG. 18) that connects the suction port side at the same time is switched.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 19A is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 19B is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a, 51a, and 52a, and the high pressure side electric expansion valve 19a and the low pressure side electric expansion. While the valve 19b is in the throttle state, the first and second electric four-way valves 31, 32 and the electric three-way valve 33 are switched to a circuit indicated by a solid line arrow.

  Thereby, as shown by the solid line arrow in FIG. 18, the first compressor 11 (→ first electric four-way valve 31) → outdoor heat exchanger 41 (→ electric three-way valve 33) → high pressure side electric expansion valve 19a. → Nozzle part 13a of ejector 13 → downstream branch part 23 → outflow side heat exchanger 52 (→ first electric four-way valve 31) → first compressor 11 circulates refrigerant in this order, and downstream branch part 23 → Low pressure side electric expansion valve 19b → first three-way joint 17a → use side heat exchanger 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → ejector 13 A cycle in which the refrigerant circulates in the order of the refrigerant suction port 13b → the downstream branching portion 23 is configured.

Therefore, the refrigerant compressed by the first compressor 11 (a ₁₉ point in FIG. 19 (a)), similarly to the first embodiment to flow into the outdoor heat exchanger 41, which is blown from the blower fan 41a refrigerator Heat exchange with outside air (outside air) to dissipate heat and condense (a ₁₉ points → b ₁₉ points). The refrigerant that has flowed out of the outdoor heat exchanger 41 flows into the high-pressure side electric expansion valve 19a via the electric three-way valve 33.

The refrigerant that has flowed into the high-pressure side electric expansion valve 19a is decompressed and expanded in an enthalpy manner and becomes an intermediate-pressure refrigerant in a gas-liquid two-phase state (b ₁₉ points → b ′ ₁₉ points). At this time, the valve opening degree of the high-pressure side electric expansion valve 19a is adjusted to a predetermined value by the first compressor 11 suction port side superheating degree of the refrigerant ₍₁₉ points f) is determined in advance.

The intermediate-pressure refrigerant flowing out from the high-pressure side electric expansion valve 19a, as in the first embodiment, is injected by isentropically decompressed and expanded by the nozzle part 13a of the ejector 13 (b _'19-point → c ₁₉ points ). The refrigerant is mixed with refrigerant discharged from the second compressor 21 (c ₁₉ point → d ₁₉ point, j ₁₉ point → d ₁₉ point), and the pressure is increased by the diffuser portion 13d (d ₁₉ point → e ₁₉ point).

  The refrigerant that has flowed out of the diffuser portion 13d flows into the downstream branch portion 23. The refrigerant that has flowed into the downstream branching portion 23 is divided into a refrigerant flow that flows into the outflow side heat exchanger 52 side and a refrigerant flow that flows into the low pressure side electric expansion valve 19b.

  Here, in the present embodiment, by setting the refrigerant passage area on the refrigerant outlet 23b side of the downstream branching portion 23 to be larger than the refrigerant passage area on the refrigerant outlet 23c side, to the outflow side heat exchanger 52 side. The refrigerant flow rate G1 flowing in is set to be larger than the refrigerant flow rate G2 flowing into the low pressure side electric expansion valve 19b.

The refrigerant that has flowed into the outflow side heat exchanger 52 from the downstream branching section 23 absorbs heat from the air in the second storage chamber circulated and blown by the blower fan 52a and evaporates (e ₁₉ point → f ₁₉ point). Thereby, the air in the second storage is cooled. Then, the refrigerant flowing out from the outflow side heat exchanger 52 is sucked into the first compressor 11 and compressed again (f ₁₉ point → a ₁₉ point).

On the other hand, the refrigerant that has flowed into the low pressure side electric expansion valve 19b from the downstream branching portion 23 is further decompressed and expanded in an enthalpy manner to lower its pressure (e ₁₉ point → h ₁₉ point). The refrigerant decompressed and expanded by the low-pressure side electric expansion valve 19b flows into the use-side heat exchanger 51 via the first three-way joint 17a, and from the air in the first storage compartment that is circulated and blown by the blower fan 51a. It absorbs heat and evaporates (h ₁₉ points → i ₁₉ points). Thereby, the air in the first storage is cooled.

  In the cooling operation mode of the present embodiment, since the electric three-way valve 33 is switched to the refrigerant flow path connecting the outdoor heat exchanger 41 and the high-pressure side electric expansion valve 19a inlet side, the first three-way The refrigerant that has flowed into the joint 17 a does not flow into the fixed throttle 18, but its entire flow rate flows into the use-side heat exchanger 51. Subsequent operations are the same as those in the first embodiment.

  Next, in the heating operation mode, the control device operates the first electric motor 11b and the blower fans 41a, 51a, and 52a to fully close the high-pressure side electric expansion valve 19a and the low-pressure side electric expansion valve 19b, The first and second electric four-way valves 31, 32 and the electric three-way valve 33 are switched to a circuit indicated by a broken line arrow, and the second electric motor 21b is stopped.

  Thereby, as shown by the broken line arrow in FIG. 18, the first compressor 11 (→ first electric four-way valve 31) → the outflow side heat exchanger 52 (→ downstream branch portion 23 → ejector 13 → second electric type Four-way valve 32) → use side heat exchanger 51 (→ first three-way joint 17a) → fixed throttle 18 (→ electric three-way valve 33) → outdoor heat exchanger 41 (→ first electric four-way valve 31) → first A cycle in which the refrigerant circulates in the order of the compressor 11 is configured.

Therefore, the refrigerant compressed by the first compressor 11 (k ₁₉ points in FIG. 19 (b)) flows into the outlet-side heat exchanger 52 via the first electric four-way valve 31, the blower fan 52a Heat is exchanged with the air in the second storage chamber that has been circulated and blown away (k ₁₉ points → k ′ ₁₉ points). Thereby, the air in the second storage is heated.

  The refrigerant that has flowed out of the outflow side heat exchanger 52 flows into the ejector 13 from the diffuser portion 13d of the ejector 13 through the downstream branch portion 23. In the heating operation mode, since the low pressure side electric expansion valve 19b is in a fully closed state, the refrigerant flowing into the downstream branching portion 23 does not flow out to the low pressure side electric expansion valve 19b side, but its total flow rate. Flows out to the diffuser portion 13d side.

The refrigerant flowing into the ejector 13 is slightly depressurized by the pressure loss when passing through the diffuser portion 13d → the refrigerant suction port 13b (k ′ ₁₉ points → m ₁₉ points). The refrigerant flowing out from the refrigerant suction port 13b of the ejector 13 flows into the use side heat exchanger 51 through the second electric four-way valve 32. The refrigerant that has flowed into the use-side heat exchanger 51 exchanges heat with the air in the first storage box circulated and blown by the blower fan 51a, dissipates heat, and condenses (m ₁₉ points → n ₁₉ points). Other operations are the same as those in the first embodiment.

  Therefore, when the ejector refrigeration cycle 400 of this embodiment is operated, in the cooling operation mode, the outdoor heat exchanger 41 functions as a radiator, and the use side heat exchanger 51 and the outflow side heat exchanger 52 serve as an evaporator. A functioning ejector refrigeration cycle is configured. Thereby, the air in the first storage can be cooled by the use side heat exchanger 51, and the air in the second storage can be cooled by the outflow side heat exchanger 52.

  Further, in the heating operation mode, the refrigerant discharged from the first compressor 11 is radiated by the outflow side heat exchanger 52 and the use side heat exchanger 51, the radiated refrigerant is decompressed and expanded by the fixed throttle 18, and the decompressed and expanded refrigerant is used. The refrigeration cycle in which the refrigerant is evaporated by the outdoor heat exchanger 41 and the evaporated refrigerant is increased again by the first compressor 11 is configured. Thereby, the internal air can be heated by the use side heat exchanger 51.

  Further, in the ejector refrigeration cycle 400 of the present embodiment, not only the same effects as (A) to (D) of the first embodiment and (F) of the fourth embodiment can be obtained, but also as follows. An effect can also be obtained.

  That is, in the cooling operation mode, the refrigerant flow rate G1 flowing from the downstream branching portion 23 to the outflow side heat exchanger 52 side at the downstream branching portion 23 flows from the downstream branching portion 23 to the fixed throttle 18 side. It is set to be larger than the flow rate G2.

  Thereby, since more refrigerant | coolants can be radiated in the heat exchanger which functions as a radiator among the outdoor heat exchanger 41 and the use side heat exchanger 51, the heat absorption amount of the refrigerant as a whole cycle, that is, the cycle The refrigeration capacity can be expanded.

(Eleventh embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 20, the electric three-way valve 33 is abolished with respect to the ejector refrigeration cycle 400 of the tenth embodiment, An example in which the three-way joint 17b and the third check valve 16c are provided will be described. Other configurations are the same as those of the tenth embodiment.

  Next, the operation of this embodiment in the above configuration will be described. In the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a, 51a and 52a, and the high pressure side electric expansion valve 19a and the low pressure side electric expansion valve 19b. Is switched to the throttle state, and the first and second electric four-way valves 31 and 32 are switched to a circuit indicated by a solid line arrow.

  Thereby, as shown by the solid line arrow in FIG. 20, the first compressor 11 (→ first electric four-way valve 31) → outdoor heat exchanger 41 (→ second three-way joint 17b) → high pressure side electric expansion valve 19a → Nozzle part 13a of ejector 13 → downstream branch part 23 → outflow side heat exchanger 52 (→ first electric four-way valve 31) → first compressor 11 circulates refrigerant in this order, and downstream branch part 23 → Low pressure side electric expansion valve 19b → first three-way joint 17a → use side heat exchanger 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → ejector 13 A cycle in which the refrigerant circulates in the order of the refrigerant suction port 13b → the downstream branching portion 23 is configured.

  Therefore, the refrigerant discharged from the first compressor 11 flows in the same manner as in the cooling operation mode of the tenth embodiment, flows into the outdoor heat exchanger 41, and dissipates heat. The refrigerant that has flowed out of the outdoor heat exchanger 41 flows into the second three-way joint 17b, and then flows into the nozzle portion 13a of the ejector 13 through the high-pressure side electric expansion valve 19a.

  At this time, the refrigerant flowing into the second three-way joint 17b does not flow out to the outlet side of the fixed throttle 18 due to the action of the third check valve 16c, and its entire flow rate flows into the nozzle portion 13a of the ejector 13. Other operations are the same as those in the refrigerant operation mode of the tenth embodiment.

  That is, in the cooling operation mode of the present embodiment, a cycle similar to that in the cooling operation mode of the tenth embodiment is configured, and operates as shown in the Mollier diagram of FIG. 19A of the tenth embodiment. As a result, in the cooling operation mode of the present embodiment, the same effect as that of the cooling operation mode of the tenth embodiment can be obtained.

  On the other hand, in the heating operation mode, the control device operates the first electric motor 11b and the blower fans 41a, 51a, and 52a to fully close the high-pressure side electric expansion valve 19a and the low-pressure side electric expansion valve 19b. 1. The second electric four-way valves 31 and 32 are switched to a circuit indicated by a broken-line arrow, and the second electric motor 21b is stopped.

  Accordingly, as indicated by the broken line arrow in FIG. 20, the first compressor 11 (→ first electric four-way valve 31) → the outflow side heat exchanger 52 (→ downstream branch portion 23 → ejector 13 → second electric type Four-way valve 32) → use side heat exchanger 51 (→ first three-way joint 17a) → fixed throttle 18 (→ third check valve 16c → second three-way joint 17b) → outdoor heat exchanger 41 (→ first electric type) A cycle in which the refrigerant circulates in the order of the four-way valve 31) → the first compressor 11 is configured.

  That is, in the heating operation mode of the present embodiment, a cycle similar to that in the heating operation mode of the tenth embodiment is configured, and operates as shown in the Mollier diagram of FIG. 19B of the tenth embodiment. As a result, in the heating operation mode of the present embodiment, the same effect as that of the heating operation mode of the tenth embodiment can be obtained.

  Furthermore, in the present embodiment, the electric three-way valve 33 is eliminated, and the third check valves 16b and 16c configured by a pure mechanical mechanism are employed to switch between the cooling operation mode and the heating operation mode. Therefore, the same effect as that of the tenth embodiment can be obtained with a simple cycle configuration.

(Twelfth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 21, the connection mode of each component device is changed with respect to the ejector refrigeration cycle 400 of the tenth embodiment, and the second compressor is operated in the heating operation mode. An example in which the refrigerant is switched to a cycle in which the refrigerant is compressed and discharged by 21 (second compression mechanism 21a) will be described.

  Specifically, the first electric four-way valve 31 of the present embodiment is provided between the discharge side of the first compressor 11 and the outdoor heat exchanger 41 and between the outflow side heat exchanger 52 and the first compressor 11 suction port. The refrigerant flow path (circuit indicated by the solid line arrow in FIG. 21), the outdoor heat exchanger 41 and the outflow side heat exchanger 52, and the first compressor 11 discharge port side and suction port The refrigerant flow paths (circuits indicated by broken line arrows in FIG. 21) that are connected at the same time are switched.

  In addition, the second electric four-way valve 32 is provided between the use-side heat exchanger 51 and the second compressor 21 suction port side and between the second compressor 21 discharge port side and the refrigerant suction port 13b side of the ejector 13 at the same time. The refrigerant flow path (circuit shown by the solid line arrow in FIG. 21), the second compressor 21 discharge side and the use side heat exchanger 51, the refrigerant suction port 13b side, and the second compressor 21 suction port side. Are switched to the refrigerant flow paths (circuits indicated by broken line arrows in FIG. 21) that are simultaneously connected to each other.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 22A is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 22B is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a, 51a, and 52a, and the high pressure side electric expansion valve 19a and the low pressure side electric expansion. While the valve 19b is in the throttle state, the first and second electric four-way valves 31, 32 and the electric three-way valve 33 are switched to a circuit indicated by a solid line arrow.

  Thereby, as shown by the solid line arrow in FIG. 21, the first compressor 11 (→ first electric four-way valve 31) → outdoor heat exchanger 41 (→ electric three-way valve 33) → high pressure side electric expansion valve 19a. → Nozzle part 13a of ejector 13 → downstream branch part 23 → outflow side heat exchanger 52 (→ first electric four-way valve 31) → first compressor 11 circulates refrigerant in this order, and downstream branch part 23 → Low pressure side electric expansion valve 19b (→ first three-way joint 17a) → use side heat exchanger 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → ejector A cycle in which the refrigerant circulates in the order of 13 refrigerant suction ports 13b → downstream branching portion 23 is configured.

  That is, in the cooling operation mode of the present embodiment, a cycle similar to that of the cooling operation mode of the tenth embodiment is configured, and operates as shown in the Mollier diagram of FIG. The operation in the cooling operation mode is the same as the operation in the cooling operation mode of the tenth embodiment (FIG. 19B). Therefore, in the cooling operation mode of this embodiment, the same effect as the cooling operation mode of the tenth embodiment can be obtained.

  Next, in the heating operation mode, the control device operates the second electric motor 21b and the blower fans 41a, 51a, and 52a to fully close the high-pressure side electric expansion valve 19a and the low-pressure side electric expansion valve 19b, The first and second electric four-way valves 31 and 32 and the electric three-way valve 33 are switched to a circuit indicated by a broken line arrow, and the first electric motor 11b is stopped.

  Accordingly, as indicated by the broken line arrow in FIG. 21, the second compressor 21 (→ second electric four-way valve 32) → the use side heat exchanger 51 (→ first three-way joint 17a) → fixed throttle 18 (→ electricity) Type three-way valve 33) → outdoor heat exchanger 41 (→ first electric four-way valve 31) → outflow side heat exchanger 52 (→ downstream branch 23 → ejector 13 → second electric four-way valve 32) → second A cycle in which the refrigerant circulates in the order of the compressor 21 is configured.

Therefore, the refrigerant compressed by the second compressor 21 (point _{22 in} FIG. 22B) flows into the use side heat exchanger 51 through the second electric four-way valve 32. The refrigerant that has flowed into the use-side heat exchanger 51 exchanges heat with the air in the first storage box circulated from the blower fan 51a to dissipate heat and condense (l ₂₂ points → n ₂₂ points). Thereby, the air in the first storage is heated.

The refrigerant radiated by the use side heat exchanger 51 flows into the fixed throttle 18 via the first three-way joint 17a and is decompressed and expanded in an enthalpy manner, similarly to the heating operation mode of the tenth embodiment ( n ₂₂ points → o ₂₂ points). Further, the refrigerant expanded under reduced pressure by the fixed throttle 18 flows into the outdoor heat exchanger 41 through the electric three-way valve 32 and absorbs heat (from point o _{22 to} point p ₂₂ ).

The refrigerant that has flowed out of the outdoor heat exchanger 41 flows into the outflow side heat exchanger 52 through the first electric four-way valve 31, and absorbs heat from the air in the second storage chamber that is circulated and blown by the blower fan 52a. evaporation (o _'22-point → p ₂₂ points). Thereby, the air in the second storage is cooled.

The refrigerant that has flowed out of the outflow side heat exchanger 52 flows into the ejector 13 from the diffuser portion 13d of the ejector 13 via the downstream branching portion 23, and is slightly depressurized due to pressure loss when flowing back through the ejector 13. (P ₂₂ point → m ₂₂ point), and flows out from the refrigerant suction port 13 b of the ejector 13. The refrigerant flowing out from the refrigerant suction port 13b is sucked into the second compressor 11 and compressed through the second electric four-way valve 32 (m ₂₂ point → l ₂₂ point).

  Therefore, in the heating operation mode of the present embodiment, the refrigerant discharged from the second compressor 21 is radiated by the use-side heat exchanger 51, the radiated refrigerant is decompressed and expanded by the fixed throttle 18, and the decompressed and expanded refrigerant is subjected to outdoor heat. A refrigeration cycle is formed in which the refrigerant is evaporated by the exchanger 41 and the outflow side heat exchanger 52, and the evaporated refrigerant is pressurized again by the second compressor 11.

  That is, in the heating operation mode of the present embodiment, the second compressor 21 performs the function of the first compressor 11 in the tenth embodiment, so that the cycle is substantially the same as in the heating operation mode of the tenth embodiment. Can be configured. As a result, the inside air can be heated by the use side heat exchanger 51, and the same effect as the heating operation mode of the tenth embodiment can be obtained.

(13th Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 23, the electric three-way valve 33 is abolished with respect to the ejector refrigeration cycle 400 of the twelfth embodiment. An example in which the three-way joint 17b and the third check valve 16c are provided will be described. Other configurations are the same as those in the twelfth embodiment.

  Next, the operation of this embodiment in the above configuration will be described. In the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a, 51a and 52a, and the high pressure side electric expansion valve 19a and the low pressure side electric expansion valve 19b. Is switched to the throttle state, and the first and second electric four-way valves 31 and 32 are switched to a circuit indicated by a solid line arrow.

  Thereby, as shown by the solid line arrow in FIG. 23, the first compressor 11 (→ first electric four-way valve 31) → outdoor heat exchanger 41 (→ second three-way joint 17b) → high pressure side electric expansion valve 19a → Nozzle part 13a of ejector 13 → downstream branch part 23 → outflow side heat exchanger 52 (→ first electric four-way valve 31) → first compressor 11 circulates refrigerant in this order, and downstream branch part 23 → Low pressure side electric expansion valve 19b (→ first three-way joint 17a) → use side heat exchanger 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → ejector A cycle in which the refrigerant circulates in the order of 13 refrigerant suction ports 13b → downstream branching portion 23 is configured.

  That is, in the cooling operation mode of the present embodiment, a cycle similar to that in the cooling operation mode of the twelfth embodiment is configured and operates as shown in the Mollier diagram of FIG. 22A of the twelfth embodiment. As a result, in the cooling operation mode of the present embodiment, the same effect as that of the cooling operation mode of the twelfth embodiment can be obtained.

  Next, in the heating operation mode, the control device operates the second electric motor 21b and the blower fans 41a, 51a, and 52a to fully close the high-pressure side electric expansion valve 19a and the low-pressure side electric expansion valve 19b, The first and second electric four-way valves 31 and 32 are switched to a circuit indicated by a broken-line arrow, and the first electric motor 11b is stopped.

  Accordingly, as indicated by the broken line arrow in FIG. 23, the second compressor 21 (→ second electric four-way valve 32) → the use-side heat exchanger 51 (→ first three-way joint 17a) → the fixed throttle 18 (→ first 3 check valve 16c → second three-way joint 17b) → outdoor heat exchanger 41 (→ first electric four-way valve 31) → outflow side heat exchanger 52 (→ downstream branch portion 23 → ejector 13 → second electric type A cycle in which the refrigerant circulates in the order of the four-way valve 32) → the second compressor 21.

  That is, in the heating operation mode of the present embodiment, a cycle similar to that in the heating operation mode of the twelfth embodiment is configured, and operates as shown in the Mollier diagram of FIG. 22B of the twelfth embodiment. As a result, in the heating operation mode of the present embodiment, the same effect as that of the heating operation mode of the twelfth embodiment can be obtained.

(14th Embodiment)
24 and 25, an example in which the ejector refrigeration cycle 600 of the present invention is applied to a cold storage container that keeps the internal temperature at a low temperature or a high temperature will be described. The cold storage in this embodiment has first and third storages that can be switched between cold storage and a second storage that can only be stored at low temperatures. FIG. 24 is an overall configuration diagram of an ejector refrigeration cycle 600 of the present embodiment.

  As shown in FIG. 24, in the ejector refrigeration cycle 600 of the present embodiment, the high pressure side temperature expansion valve 19a is abolished with respect to the ejector refrigeration cycle 200 of the fourth embodiment, and the upstream branch portion 22 and An auxiliary heat exchanger 53 is provided between the fixed throttle 18 which is a refrigerant decompression unit.

  The auxiliary heat exchanger 53 exchanges heat between the refrigerant passing through the inside and the air in the third storage box circulated and blown by the blower fan 53a. The blower fan 53a is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the control device. Moreover, in this embodiment, the heat exchange performance of the outdoor heat exchanger 41 is reduced with respect to the above-described embodiment. Other configurations are the same as those of the fourth embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 25A is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 25B is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b, the blower fans 41a and 51a to 53a, and the first and second electric four-way valves 31 and 32. Is switched to the circuit indicated by the solid arrow.

  Accordingly, as indicated by the solid line arrow in FIG. 24, the first compressor 11 (→ first electric four-way valve 31) → outdoor heat exchanger 41 → upstream branching portion 22 → second check valve 16b → ejector 13 The refrigerant circulates in the order of the nozzle part 13a (→ the first electric four-way valve 31) → the outflow side heat exchanger 52 → the first compressor 11, and the upstream side branch part 22 → the auxiliary heat exchanger 53 → the fixed throttle 18. → Use side heat exchanger 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → refrigerant suction port 13b of the ejector 13 (→ first electric four-way valve 31) ) → outflow side heat exchanger 52 → first compressor 11 in this order.

Therefore, the refrigerant compressed by the first compressor 11 (a ₂₅ point in FIG. 25 (a)) via the first electric four-way valve 31, flows into the outdoor heat exchanger 41, the blower fan 41a Heat is exchanged with the blown outside air (outside air) to dissipate heat (a ₂₅ points → b ₁₆ points).

  The refrigerant that has flowed out of the outdoor heat exchanger 41 flows into the upstream branch portion 22 and flows into the auxiliary heat exchanger 53 side and the refrigerant flow that flows into the nozzle portion 13a side of the ejector 13 through the check valve 17c. It is divided into the refrigerant flow. In this embodiment as well, as in the fourth embodiment, the flow characteristics (pressure loss characteristics) of the nozzle portion 13a and the fixed throttle 18 are determined so that the flow ratio Ge / Gnoz becomes the optimum flow ratio. ing.

The refrigerant that has flowed from the upstream branch portion 22 to the nozzle portion 13a side of the ejector 13 via the second check valve 16b is decompressed and expanded in an isentropic manner at the nozzle portion 13a of the ejector 13 as in the fourth embodiment. to be injected (b ₂₅ points → c ₂₅ points), is mixed with the second compressor 21 discharge refrigerant ₍₂₅ points → d ₂₅ points c, j ₂₅ points → d ₂₅ points), further, boosting at the diffuser portion 13d (D ₂₅ points → e ₂₅ points).

Refrigerant flowing out of the diffuser unit 13d, the outflow-side heat exchanger 52 flows into the blower fan 52a by such refrigerant is evaporated by absorbing heat from the second storage-compartment air circulating blower (e ₂₅ points → f ₂₅ points). Thereby, the air in the second storage is cooled. The refrigerant flowing out of the outflow side heat exchanger 52 is sucked into the first compressor 11 and compressed again (f ₂₅ point → a ₂₅ point).

On the other hand, the refrigerant that has flowed out from the upstream branching section 22 to the auxiliary heat exchanger 53 side performs heat exchange with the air in the third storage chamber circulated from the blower fan 53a to dissipate heat, thereby further reducing the enthalpy (b). ₂₅ points → b _'25 points). Thereby, the air in the third storage is heated. The refrigerant that has flowed out of the auxiliary heat exchanger 53 is decompressed and expanded in an enthalpy manner at the fixed throttle 18 to reduce its pressure (b ′ ₂₅ point → h ₂₅ point). Subsequent operations are the same as those in the fourth embodiment.

  Next, in the heating operation mode, the control device operates the first electric motor 11b and the blower fans 41a and 51a to 53a, and switches the first and second electric four-way valves 31 and 32 to circuits indicated by broken line arrows. Then, the second electric motor 21b is stopped.

  Accordingly, as indicated by the broken line arrow in FIG. 24, the first compressor 11 (→ first electric four-way valve 31 → ejector 13 → second electric four-way valve 32) → use side heat exchanger 51 → fixed throttle 18 -> Auxiliary heat exchanger 53-> upstream branch section 22-> outdoor heat exchanger 41 (-> first electric four-way valve 31)-> outflow side heat exchanger 52-> first compressor 11 Is done.

Therefore, the refrigerant compressed by the first compressor 11 (k ₂₅ points in FIG. 25 (b)), as well as the heating operation mode of the fourth embodiment, is slightly reduced in pressure during flow back through the ejector 13 (K ₂₅ point → m ₂₅ point), it flows into the use side heat exchanger 51 through the second electric four-way valve 32.

The refrigerant flowing into the use-side heat exchanger 51 exchanges heat with the air in the first storage box circulated from the blower fan 51a to dissipate heat and condense (m ₂₅ points → n ₂₅ points). Thereby, the air in the first storage is heated. The refrigerant radiated by the use side heat exchanger 51 flows into the fixed throttle 18 and is decompressed and expanded in an enthalpy manner (n ₂₅ points → o ₂₅ points) and flows into the auxiliary heat exchanger 53.

The refrigerant that has flowed into the auxiliary heat exchanger 53 absorbs heat from the air in the third storage box circulated from the blower fan 53a to increase its enthalpy (o ₂₅ points → o ′ ₂₅ points). Thereby, the air in the third storage is cooled. The refrigerant that has flowed out of the auxiliary heat exchanger 53 flows into the outdoor heat exchanger 41 through the upstream branching portion 22.

  At this time, the refrigerant that has flowed into the upstream branching portion 22 is caused by the pressure loss in the refrigerant flow path from the upstream branching portion 22 → the second check valve 16 b → the nozzle portion 13 a of the ejector 13 → the refrigerant suction port 13 b to the upstream side. Since it is larger than the pressure loss of the refrigerant flow path from the branching section 22 → the outdoor heat exchanger 41 → the first electric four-way valve 31 → the outflow side heat exchanger 52 → the diffuser section 13 d of the ejector 13 → the refrigerant suction port 13 b, Substantially the entire flow rate flows out to the outdoor heat exchanger 41 side.

The refrigerant that has flowed into the outdoor heat exchanger 41 absorbs heat from outside air (outside air) blown by the blower fan 41a and increases enthalpy (o ′ ₂₅ points → o ″ ₂₅ points). The refrigerant flowing out of the refrigerant flows into the outflow side heat exchanger 52 through the first electric four-way valve 31, absorbs heat from the air in the second storage chamber circulated by the blower fan 52a, and further increases enthalpy. (O ” ₂₅ points → p ₂₅ points). Thereby, the air in the second storage is cooled.

  Other operations are the same as those in the fourth embodiment. Therefore, when the ejector refrigeration cycle 600 of the present embodiment is operated, in the cooling operation mode, the outdoor heat exchanger 41 and the auxiliary heat exchanger 53 function as a radiator, and the first usage side heat exchanger 51 and the outflow side are operated. An ejector refrigeration cycle in which the heat exchanger 52 functions as an evaporator is configured.

  Thereby, the air in the first storage can be cooled by the use-side heat exchanger 51, the air in the second storage can be cooled by the outflow-side heat exchanger 52, and the third heat can be cooled by the auxiliary heat exchanger 53. The air in the storage can be heated.

  In the heating operation mode, the refrigerant discharged from the first compressor 11 is radiated by the use-side heat exchanger 51, the radiated refrigerant is decompressed and expanded by the fixed throttle 18, and the decompressed and expanded refrigerant is supplemented by the auxiliary heat exchanger 53, A refrigeration cycle is configured in which the refrigerant is evaporated by the outdoor heat exchanger 41 and the outflow side heat exchanger 52, and the evaporated refrigerant is pressurized again by the first compressor 11.

  Thereby, the air in the first storage can be heated by the use-side heat exchanger 51, the air in the second storage can be cooled by the outflow-side heat exchanger 52, and the third heat can be cooled by the auxiliary heat exchanger 53. The air in the storage can be cooled.

  Furthermore, in the ejector refrigeration cycle 600 of the present embodiment, not only can the same effects as (A) to (D) of the first embodiment and (G) and (H) of the fourth embodiment be obtained, The following excellent effects can also be obtained.

  That is, during the cooling operation mode, the enthalpy of the refrigerant flowing into the fixed throttle 18 can be reduced by the action of the auxiliary heat exchanger 53, and therefore the enthalpy of the inlet side refrigerant of the use side heat exchanger 51 acting as an evaporator. And the enthalpy difference between the outlet side refrigerant and the enthalpy of the outlet side refrigerant can be expanded to increase the refrigeration capacity.

  Furthermore, the auxiliary heat exchanger 53 does not radiate the refrigerant that has flowed from the upstream branching portion 22 to the nozzle portion 13a side of the ejector 13. Therefore, the enthalpy of the refrigerant flowing into the nozzle portion 13a is not unnecessarily reduced by reducing the heat exchange performance of the outdoor heat exchanger 41 as in this embodiment. Therefore, in this embodiment as well as (I) and (J) of the eighth embodiment, a further COP improvement effect can be obtained.

(Fifteenth embodiment)
In the present embodiment, the ejector-type refrigeration is changed to a cold storage container in which the arrangement of the outflow heat exchanger 52 is changed with respect to the fourteenth embodiment so that all of the first to third storage containers can be switched to cold storage. An example in which the cycle 600 is applied will be described. Specifically, as shown in the overall configuration diagram of FIG. 26, the outflow side heat exchanger 52 of the present embodiment includes a diffuser portion 13d outlet of the ejector 13 and one refrigerant inlet / outlet of the first electric four-way valve 31. It is arranged between.

  Therefore, the first electric four-way valve 31 of this embodiment is similar to that of the fifth embodiment between the outlet of the first compressor 11 and the outdoor heat exchanger 41 and the first heat exchanger 52 and the first heat exchanger 52. The refrigerant flow path (circuit shown by the solid line arrow in FIG. 26) that connects the compressor 11 and the suction port side at the same time, the discharge side of the first compressor 11 and the outflow side heat exchanger 52, and outdoor heat exchange. The refrigerant flow path (the circuit indicated by the broken line arrow in FIG. 26) that connects the compressor 41 and the first compressor 11 at the same time is switched. Other configurations are the same as those in the fourteenth embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 27A is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 27B is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b, the blower fans 41a and 51a to 53a, and the first and second electric four-way valves 31 and 32. Is switched to the circuit indicated by the solid arrow.

  Thereby, as shown by the solid line arrow in FIG. 26, the first compressor 11 (→ the first electric four-way valve 31) → the outdoor heat exchanger 41 → the upstream branch portion 22 (→ the second check valve 16b) → The refrigerant circulates in the order of the nozzle portion 13a of the ejector 13 → the outflow side heat exchanger 52 (→ the first electric four-way valve 31) → the first compressor 11, and the upstream side branch portion 22 → the auxiliary heat exchanger 53 → fixed. Restriction 18 → use side heat exchanger 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → refrigerant suction port 13b of the ejector 13 → outflow side heat exchanger 52 A cycle in which the refrigerant circulates in the order of (→ first electric four-way valve 31) → first compressor 11 is configured.

  That is, in the cooling operation mode of the present embodiment, a cycle that is exactly the same as that of the cooling operation mode of the fourteenth embodiment is configured, and operates as shown in the Mollier diagram of FIG. The operation in the cooling operation mode is the same as the operation in the cooling operation mode of the fourteenth embodiment (FIG. 25A). Therefore, in the cooling operation mode of the present embodiment, the same effect as that of the cooling operation mode of the fourteenth embodiment can be obtained.

  Next, in the heating operation mode, the control device operates the first electric motor 11b and the blower fans 41a and 51a to 53a, and switches the first and second electric four-way valves 31 and 32 to circuits indicated by broken line arrows. Then, the second electric motor 21b is stopped.

  Accordingly, as indicated by the broken line arrow in FIG. 26, the first compressor 11 (→ first electric four-way valve 31) → outflow side heat exchanger 52 (→ ejector 13 → second electric four-way valve 32) → use The refrigerant circulates in the order of the side heat exchanger 51 → the fixed throttle 18 → the auxiliary heat exchanger 53 (→ the upstream branch portion 22) → the outdoor heat exchanger 41 (→ the first electric four-way valve 31) → the first compressor 11. A cycle is configured.

Therefore, the refrigerant compressed by the first compressor 11 (k ₂₇ points in FIG. 27 (b)) flows into the outlet-side heat exchanger 52 via the first electric four-way valve 31, the blower fan 52a Heat is exchanged with the air in the second storage chamber that has been circulated and radiated (k ₂₇ points → k ′ ₂₇ points). Thereby, the air in the second storage is heated.

The refrigerant radiated by the outflow side heat exchanger 52 is slightly depressurized (k ′ ₂₇ points → m ₂₇ points) when it flows backward in the ejector 13, and the use side heat is passed through the second electric four-way valve 32. It flows into the exchanger 51. Refrigerant flowing into the utilization-side heat exchanger 51, the blower fan 51a within the first exchanging heat with air storage chamber that is circulated blown by the heat dissipation to condense (m ₂₇ points → n ₂₇ points). Thereby, the air in the first storage is heated.

As in the fourteenth embodiment, the refrigerant that has flowed out from the use side heat exchanger 51 is decompressed and expanded in an enthalpy manner by the fixed throttle 18 (n ₂₇ points → o ₂₇ points), and the auxiliary heat exchanger 53 3. Heat is absorbed from the air in the storage (o ₂₇ points → o ′ ₂₇ points), and the outdoor heat exchanger 41 absorbs heat from the outside air (o ′ ₂₇ points → p ₂₇ points). Further, the refrigerant flowing out of the outdoor heat exchanger 41 is sucked into the first compressor 11 through the first electric four-way valve 31 and compressed again.

  Other operations are the same as those in the heating operation mode of the fourteenth embodiment. Therefore, in the heating operation mode of the present embodiment, the refrigerant discharged from the first compressor 11 is radiated by the outflow side heat exchanger 52 and the use side heat exchanger 51, and the radiated refrigerant is decompressed and expanded by the fixed throttle 18, A refrigerant cycle in which the refrigerant expanded under reduced pressure is evaporated by the auxiliary heat exchanger 53 and the outdoor heat exchanger 41 and the evaporated refrigerant is pressurized again by the first compressor 11 is configured.

  Thereby, the air in the first storage can be heated by the use side heat exchanger 51, the air in the second storage can be heated by the outflow side heat exchanger 52, and the third storage can be performed by the auxiliary heat exchanger 53. The internal air can be cooled, and the same effect as in the heating operation mode of the fourteenth embodiment can be obtained.

(Sixteenth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 28, the connection mode of each component device is changed with respect to the ejector refrigeration cycle 600 of the fourteenth embodiment, and the second compressor 21 is changed in the heating operation mode. An example in which the cycle is switched to a cycle in which the refrigerant is compressed and discharged by the (second compression mechanism 21a) will be described.

  Specifically, the outflow side heat exchanger 52 of the present embodiment is provided between the outlet of the diffuser portion 13d of the ejector 13 and one refrigerant inflow / outlet of the first electric four-way valve 31, as in the fifteenth embodiment. Has been placed.

  The first electric four-way valve 31 simultaneously connects the first compressor 11 outlet side and the outdoor heat exchanger 41 and the outflow side heat exchanger 52 and the first compressor 11 suction side. The refrigerant flow path (circuit indicated by the solid line arrow in FIG. 28), the outdoor heat exchanger 41 and the outflow side heat exchanger 52, and the first compressor 11 outlet side and inlet side are simultaneously connected. The refrigerant flow path (circuit indicated by the broken line arrow in FIG. 28) is switched.

  Further, the second electric four-way valve 32 is provided between the use-side heat exchanger 51 and the second compressor 21 suction port side and between the second compressor 21 discharge port side and the refrigerant suction port 13b side of the ejector 13 at the same time. The refrigerant flow path (circuit shown by the solid line arrow in FIG. 28), the second compressor 21 discharge side and the use side heat exchanger 51, the refrigerant suction port 13b side, and the second compressor 21 suction port side. Are switched to the refrigerant flow path (circuit indicated by the broken line arrow in FIG. 28). Other configurations are the same as those of the 144th embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 29A is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 29B is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b, the blower fans 41a and 51a to 53a, and the first and second electric four-way valves 31 and 32 are operated. Switch to the circuit indicated by the solid arrow.

  Thereby, as shown by the solid line arrow in FIG. 28, the first compressor 11 (→ the first electric four-way valve 31) → the outdoor heat exchanger 41 → the upstream branch section 22 (→ the second check valve 16b) → The refrigerant circulates in the order of the nozzle portion 13a of the ejector 13 → the outflow side heat exchanger 52 (→ the first electric four-way valve 31) → the first compressor 11, and the upstream side branch portion 22 → the auxiliary heat exchanger 53 → fixed. Restriction 18 → use side heat exchanger 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → refrigerant suction port 13b of the ejector 13 → outflow side heat exchanger 52 A cycle in which the refrigerant circulates in the order of (→ first electric four-way valve 31) → first compressor 11 is configured.

  That is, in the cooling operation mode of the present embodiment, a cycle exactly the same as that of the fourteenth embodiment is configured and operates as shown in the Mollier diagram of FIG. The operation in the cooling operation mode is the same as the operation in the cooling operation mode of the fourteenth embodiment (FIG. 25A). Therefore, in the cooling operation mode of the present embodiment, the same effect as that of the cooling operation mode of the fourteenth embodiment can be obtained.

  Next, in the heating operation mode, the control device operates the second electric motor 21b and the blower fans 41a and 51a to 53a, and switches the first and second electric four-way valves 31 and 32 to circuits indicated by broken line arrows. Then, the first electric motor 11b is stopped.

  As a result, as indicated by the broken line arrow in FIG. 28, the second compressor 21 (→ second electric four-way valve 32) → the use side heat exchanger 51 → the fixed throttle 18 → the auxiliary heat exchanger 53 → the upstream branch section. Cycle in which refrigerant circulates in the order of 22 → outdoor heat exchanger 41 (→ first electric four-way valve 31) → outflow side heat exchanger 52 (→ ejector 13 → second electric four-way valve 32) → second compressor 21 Is configured.

Therefore, the refrigerant compressed by the second compressor 21 (l ₂₉ points in FIG. 29 (b)) flows into the use-side heat exchanger 51 via a second electric four-way valve 32, the blower fan 51a Heat is exchanged with the air in the first storage chamber that has been circulated and radiated (l ₂₉ points → n ₂₉ points). Thereby, the air in the first storage is heated.

The refrigerant that has flowed out of the use side heat exchanger 51 is decompressed and expanded in an enthalpy manner by the fixed throttle 18 (n ₂₉ points → o ₂₉ points) and flows into the auxiliary heat exchanger 53 as in the fourteenth embodiment. . The refrigerant flowing into the auxiliary heat exchanger 53 absorbs heat from the air in the third storage box circulated from the blower fan 53a (o ₂₉ points → o ′ ₂₉ points). Thereby, the air in the third storage is cooled.

The refrigerant that has flowed out of the auxiliary heat exchanger 53 flows into the outdoor heat exchanger 41 through the upstream branching portion 22 as in the fourteenth embodiment. The refrigerant flowing into the outdoor heat exchanger 41 exchanges heat with the outside air (outside air) blown from the blower fan 41a and absorbs heat (o ′ ₂₉ points → o ″ ₂₉ points).

Furthermore, the refrigerant that has flowed out of the outdoor heat exchanger 41 flows into the outflow side heat exchanger 52 via the first electric four-way valve 31, and absorbs heat from the air in the second storage chamber that is circulated and blown from the blower fan 52a. (O ″ ₂₉ points → p ₂₉ points) Thereby, the air in the second storage is cooled.

Refrigerant flowing out from the outflow-side heat exchanger 52 flows into the ejector 13 through the first electric four-way valve 31, it is slightly reduced in pressure when reverse flow through the ejector 13 (p ₁₁ points → m ₁₁ points ). Further, the air is sucked into the second compressor 21 through the second electric four-way valve 32 and compressed again. Other operations are the same as those in the fourteenth embodiment.

  Therefore, in the heating operation mode of the present embodiment, the refrigerant discharged from the second compressor 21 is radiated by the use side heat exchanger 51, the radiated refrigerant is decompressed and expanded by the fixed throttle 18, and the decompressed and expanded refrigerant is supplemented by heat. A refrigeration cycle is configured in which the refrigerant is evaporated in the exchanger 53, the outdoor heat exchanger 41, and the outflow side heat exchanger 52, and the evaporated refrigerant is pressurized again in the second compressor 21.

  That is, in the heating operation mode of the present embodiment, the second compressor 21 performs the function of the first compressor 11 in the fourteenth embodiment, so that the cycle is substantially the same as in the heating operation mode of the fourteenth embodiment. Can be configured.

  As a result, the air in the first storage can be heated by the use side heat exchanger 51, the air in the second storage can be cooled by the outflow side heat exchanger 52, and the third storage can be made by the auxiliary heat exchanger 53. The internal air can be cooled, and the same effect as in the heating operation mode of the fourteenth embodiment can be obtained.

(17th Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 30, the connection mode of each component device is changed with respect to the ejector refrigeration cycle 600 of the fourteenth embodiment, and the second compressor 21 is changed in the heating operation mode. The cycle is switched to a cycle in which the refrigerant is compressed and discharged by the (second compression mechanism 21a). In the ejector refrigeration cycle 600 of the present embodiment, the air in the second storage compartment is neither heated nor cooled during the heating operation mode.

  Specifically, the outflow side heat exchanger 52 of the present embodiment is disposed between one refrigerant inflow / outlet of the first electric four-way valve 31 and the suction port of the first compressor 11.

  The first electric four-way valve 31 simultaneously connects the discharge side of the first compressor 11 and the outdoor heat exchanger 41 and the outlet side of the diffuser section of the ejector 13 and the outflow side heat exchanger 52. Between the refrigerant flow path (circuit shown by the solid line arrow in FIG. 30), the outdoor heat exchanger 41 and the diffuser part outlet side of the ejector 13, and between the outflow side heat exchanger 52 and the first compressor 11 inlet side. Are switched to the refrigerant flow paths (circuits indicated by broken line arrows in FIG. 30).

  Further, the second electric four-way valve 32 is provided between the use-side heat exchanger 51 and the second compressor 21 suction port side and between the second compressor 21 discharge port side and the refrigerant suction port 13b side of the ejector 13 simultaneously. The refrigerant flow path (circuit shown by the solid line arrow in FIG. 30), the second compressor 21 discharge side and the use side heat exchanger 51, the refrigerant suction port 13b side, and the second compressor 21 suction port side. Are switched to the refrigerant flow paths (circuits indicated by broken line arrows in FIG. 30). Other configurations are the same as those in the fourteenth embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 31 (a) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 31 (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b, the blower fans 41a and 51a to 53a, and the first and second electric four-way valves 31 and 32 are operated. Switch to the circuit indicated by the solid arrow.

  Thereby, as shown by the solid line arrow in FIG. 30, the first compressor 11 (→ first electric four-way valve 31) → outdoor heat exchanger 41 → high pressure side electric expansion valve 19a → upstream branching section 22 (→ The refrigerant circulates in the order of the second check valve 16b) → the nozzle part 13a of the ejector 13 (→ the first electric four-way valve 31) → the outflow side heat exchanger 52 → the first compressor 11, and the upstream side branch part 22 → Fixed throttle 18 → Use side heat exchanger 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → refrigerant suction port 13b of the ejector 13 (→ first electric A cycle in which the refrigerant circulates in the order of the four-way valve 31) → the outflow side heat exchanger 52 → the first compressor 11.

  That is, in the cooling operation mode of the present embodiment, a cycle that is exactly the same as that of the cooling operation mode of the fourteenth embodiment is configured, and operates as shown in the Mollier diagram of FIG. The operation in the cooling operation mode is the same as the operation in the cooling operation mode of the fourteenth embodiment (FIG. 25 (a)). Therefore, in the cooling operation mode of the present embodiment, the same effect as that of the cooling operation mode of the fourteenth embodiment can be obtained.

  Next, in the heating operation mode, the control device operates the second electric motor 21b and the blower fans 41a, 51a, and 53a, and switches the first and second electric four-way valves 31 and 32 to circuits indicated by broken line arrows, While the high pressure side electric expansion valve 19a is brought into the throttle state, the first electric motor 11b and the blower fan 52a are stopped.

  Thereby, as shown by the broken line arrow in FIG. 30, the second compressor 21 (→ second electric four-way valve 32) → the use side heat exchanger 51 → the fixed throttle 18 → the auxiliary heat exchanger 53 → the upstream side branch section. A cycle in which the refrigerant circulates is configured in the order of 22 → outdoor heat exchanger 41 (→ first electric four-way valve 31 → ejector 13 → second electric four-way valve 32) → second compressor 21.

Therefore, the refrigerant compressed by the second compressor 21 (l ₃₁ points in FIG. 31 (b)) flows into the use-side heat exchanger 51 via a second electric four-way valve 32, the blower fan 51a Heat is exchanged with the air in the first storage box that has been circulated and radiated to dissipate heat (from ₃₁ points to ₃₁ points). Thereby, the air in the first storage is heated.

The refrigerant that has flowed out of the use-side heat exchanger 51 is decompressed and expanded in an isenthalpy manner at the fixed restrictor 18 (n ₃₁ point → o ₃₁ point) and flows into the auxiliary heat exchanger 53 as in the fourteenth embodiment. . The refrigerant that has flowed into the auxiliary heat exchanger 53 absorbs heat from the air in the third storage box blown from the blower fan 53a (o ₃₁ point → o ′ ₃₁ point). Thereby, the air in the third storage is cooled.

The refrigerant that has flowed out of the auxiliary heat exchanger 53 flows into the outdoor heat exchanger 41 through the upstream branching portion 22 as in the fourteenth embodiment. The refrigerant flowing into the outdoor heat exchanger 41 exchanges heat with the outside air (outside air) blown from the blower fan 41a and absorbs heat (o ′ ₃₁ point → p ₃₁ point).

The refrigerant flowing out from the outdoor heat exchanger 41, via the first electric four-way valve 31, flows into the ejector 13, is slightly reduced in pressure during flow back through the ejector 13 (p ₃₁ points → m ₃₁ points) Then, it is sucked into the second compressor 21 through the second electric four-way valve 32 and compressed again. Other operations are the same as those in the fourteenth embodiment.

  Therefore, in the heating operation mode of the present embodiment, the refrigerant discharged from the second compressor 21 is radiated by the use side heat exchanger 51, the radiated refrigerant is decompressed and expanded by the fixed throttle 18, and the decompressed and expanded refrigerant is supplemented by heat. A refrigeration cycle is formed in which the refrigerant is evaporated by the exchanger 53 and the outdoor heat exchanger 41, and the evaporated refrigerant is pressurized again by the second compressor 21.

  Thereby, in the heating operation mode of the present embodiment, the second compressor 21 fulfills the function of the first compressor 11 in the fourteenth embodiment although the air in the second storage chamber cannot be cooled or heated. Thus, the use-side heat exchanger 51 can heat the air in the first storage compartment, and the auxiliary heat exchanger 53 can cool the air in the third storage compartment.

(Eighteenth embodiment)
In the present embodiment, an ejector refrigeration cycle 700 in which an internal heat exchanger 36 is added to the ejector refrigeration cycle 200 of the fourth embodiment will be described as shown in the overall configuration diagram of FIG. In the cooling operation mode, the internal heat exchanger 36 includes a refrigerant in a decompression / expansion process that passes through the fixed throttle 18 as a high-pressure side refrigerant flow path, and a second compression mechanism 21a suction refrigerant that passes through the low-pressure side refrigerant flow path 36b. Heat exchange between them.

  As a specific configuration of the internal heat exchanger 36, a double-tube heat exchanger configuration in which a fixed throttle 18 made of a capillary tube or the like is disposed inside an outer tube that forms the low-pressure side refrigerant flow path 36b. Is adopted. Of course, a configuration in which the fixed throttle 18 and the refrigerant pipe forming the low-pressure side refrigerant flow path 36b are brazed and joined to exchange heat may be employed.

  Therefore, the second electric four-way valve 32 of the present embodiment is provided between the use side heat exchanger 51 and the low pressure side refrigerant flow path 36b of the internal heat exchanger 36 and between the discharge port side of the second compressor 21 and the ejector 13. A refrigerant flow path (a circuit indicated by a solid arrow in FIG. 32) that connects the refrigerant suction port 13b at the same time, a space between the refrigerant suction port 13b and the use-side heat exchanger 51, and a discharge port side of the second compressor 21 The refrigerant flow path (circuit indicated by the broken line arrow in FIG. 32) that connects the low pressure side refrigerant flow path 36b at the same time is switched. Other configurations are the same as those of the fourth embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 33 (a) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 33 (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a, 51a, and 52a, and the first and second electric four-way valves 31 and 32 are operated. The circuit is switched to the circuit indicated by the solid arrow, and the high-pressure electric expansion valve 19a is in the throttle state.

  Thereby, as shown by the solid line arrow in FIG. 32, the first compressor 11 (→ the first electric four-way valve 31) → the outdoor heat exchanger 41 → the high-pressure side electric expansion valve 19a → the upstream branch section 22 (→ The refrigerant circulates in the order of the second check valve 16b) → the nozzle part 13a of the ejector 13 (→ the first electric four-way valve 31) → the outflow side heat exchanger 52 → the first compressor 11, and the upstream side branch part 22 → Fixed throttle 18 → Use side heat exchanger 51 (→ second electric four-way valve 32) → Low pressure side refrigerant flow path 36b of the internal heat exchanger 36 → Second compressor 21 (→ second electric four-way valve 32) A cycle in which the refrigerant circulates in the order of the refrigerant suction port 13 b of the ejector 13, the outflow side heat exchanger 52, and the first compressor 11.

Therefore, (a ₃₃ point in FIG. 33 (a)) the refrigerant compressed in the first compressor 11, at the upstream side branch portion 22 as in the fourth embodiment, the outflow to the nozzle portion 13a of the ejector 13 And a flow that flows out to the internal heat exchanger 36 (fixed throttle 18) side.

The high-pressure refrigerant flowing into the internal heat exchanger 36 (fixed throttle 18) from the upstream branching section 22 exchanges heat with the refrigerant sucked by the second compressor 21 flowing through the low-pressure side refrigerant flow path 35b, thereby reducing its enthalpy. (B ₃₃ points → h ₃₃ points). Along with this, the enthalpy of the refrigerant sucked by the second compressor 21 increases (i ₃₃ points → i ′ ₃₃ points).

  In other words, the refrigerant passing through the fixed throttle 18 is cooled to the same temperature as the refrigerant sucked by the second compression mechanism 21a while expanding under reduced pressure, thereby reducing its enthalpy. Thereby, the enthalpy of the refrigerant | coolant which flows in into the utilization side heat exchanger 51 which functions as an evaporator can be decreased with respect to 4th Embodiment. Other operations are the same as those in the fourth embodiment.

  Therefore, in the cooling operation mode of the present embodiment, an ejector type refrigeration cycle is configured in which the outdoor heat exchanger 41 functions as a radiator and the use side heat exchanger 51 and the outflow side heat exchanger 52 function as an evaporator. . Thereby, the air in the first storage can be cooled by the use side heat exchanger 51, and the air in the second storage can be cooled by the outflow side heat exchanger 52.

  Furthermore, in the cooling operation mode of the present embodiment, not only can the same effect as in the cooling operation mode of the fourth embodiment be obtained, but (I) and (I) of the eighth embodiment can be obtained by the action of the internal heat exchanger 36. The COP improvement effect equivalent to J) can be obtained.

  Next, in the heating operation mode, the control device operates the first electric motor 11b and the blower fans 41a, 51a, and 52a, and switches the first and second electric four-way valves 31 and 32 to circuits indicated by broken line arrows, While the high pressure side electric expansion valve 19a is in the throttle state, the second electric motor 21b is stopped.

  Thereby, as shown by the broken line arrow in FIG. 32, the first compressor 11 (→ first electric four-way valve 31 → ejector 13 → second electric four-way valve 32) → use side heat exchanger 51 → fixed throttle 18 → Upstream side branching section 22 → High pressure side electric expansion valve 19a → Outdoor heat exchanger 41 (→ First electric four-way valve 31) → Outflow side heat exchanger 52 → Cycle in which refrigerant circulates in the order of the first compressor 11 Is configured.

  Here, in the heating operation mode of the present embodiment, since the second electric motor 21b is stopped and the second compressor 21 does not exhibit the refrigerant discharge capability, the refrigerant discharged from the second compressor 21 is used as the internal heat exchanger 36. The low-pressure side refrigerant flow path 36b is not circulated. Therefore, the enthalpy of the refrigerant in the decompression / expansion process at the fixed throttle 18 does not increase or decrease.

  That is, in the heating operation mode of the present embodiment, a cycle that is exactly the same as that of the heating operation mode of the fourth embodiment is configured, and operates as shown in the Mollier diagram of FIG. The operation in the heating operation mode is the same as the operation in the heating operation mode of the fourth embodiment (FIG. 7B). Therefore, in the heating operation mode of this embodiment, the same effect as the heating operation mode of the fourth embodiment can be obtained.

(Nineteenth embodiment)
As shown in the overall configuration diagram of FIG. 34, the ejector refrigeration cycle 700 of the present embodiment has an internal heat exchanger 36 similar to that of the eighteenth embodiment added to the ejector refrigeration cycle 200 of the fifth embodiment. It is a thing. Therefore, in the present embodiment, both the first and second storages can be switched between cold storage and cold storage. The second electric four-way valve 32 of the present embodiment also switches the refrigerant flow path as in the eighteenth embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 35 (a) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 35 (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a, 51a, and 52a, and the first and second electric four-way valves 31 and 32 are operated. While switching to the circuit indicated by the solid line arrow, the high pressure side electric expansion valve 19a is brought into the throttle state.

  As a result, as shown by the solid line arrow in FIG. 34, the first compressor 11 (→ first electric four-way valve 31) → outdoor heat exchanger 41 → high pressure side electric expansion valve 19a → upstream branching section 22 (→ The refrigerant circulates in the order of the second check valve 16 b) → the nozzle portion 13 a of the ejector 13 → the outflow side heat exchanger 52 (→ the first electric four-way valve 31) → the first compressor 11, and the upstream branch portion 22. → Fixed throttle 18 → Use side heat exchanger 51 (→ second electric four-way valve 32) → Low pressure side refrigerant flow path 36b of the internal heat exchanger 36 → Second compressor 21 (→ second electric four-way valve 32) A cycle in which the refrigerant circulates in the order of the refrigerant suction port 13 b of the ejector 13, the outflow side heat exchanger 52, and the first compressor 11.

  That is, in the cooling operation mode of the present embodiment, a cycle exactly the same as that of the eighteenth embodiment is configured, and operates as shown in the Mollier diagram of FIG. The operation in the cooling operation mode is the same as the operation in the cooling operation mode of the eighteenth embodiment (FIG. 33 (a)). Therefore, in the cooling operation mode of this embodiment, the same effect as that of the cooling operation mode of the eighteenth embodiment can be obtained.

  Next, in the heating operation mode, the control device operates the first electric motor 11b and the blower fans 41a, 51a, and 52a, and switches the first and second electric four-way valves 31 and 32 to circuits indicated by broken line arrows, While the high pressure side electric expansion valve 19a is in the throttle state, the second electric motor 21b is stopped.

  As a result, as indicated by the broken line arrow in FIG. 34, the first compressor 11 (→ first electric four-way valve 31) → outflow side heat exchanger 52 (→ ejector 13 → second electric four-way valve 32) → use Refrigerant circulates in the order of side heat exchanger 51 → fixed throttle 18 → upstream branch portion 22 → high pressure side electric expansion valve 19a → outdoor heat exchanger 41 (→ first electric four-way valve 31) → first compressor 11 A cycle is configured.

  Here, in the heating operation mode of the present embodiment, since the second electric motor 21b is stopped and the second compressor 21 does not exhibit the refrigerant discharge capability, the refrigerant discharged from the second compressor 21 is used as the internal heat exchanger 36. The low-pressure side refrigerant flow path 36b is not circulated. Therefore, the enthalpy of the refrigerant in the decompression / expansion process at the fixed throttle 18 does not increase or decrease.

  That is, in the heating operation mode of the present embodiment, a cycle exactly the same as that of the heating operation mode of the fifth embodiment is configured, and operates as shown in the Mollier diagram of FIG. The operation in the heating operation mode is the same as the operation in the heating operation mode of the fifth embodiment (FIG. 9B). Therefore, in the heating operation mode of the present embodiment, the same effect as that of the heating operation mode of the fifth embodiment can be obtained.

(20th embodiment)
In the ejector refrigeration cycle 700 of the present embodiment, an internal heat exchanger 36 similar to that of the eighteenth embodiment is added to the ejector refrigeration cycle 200 of the sixth embodiment, as shown in the overall configuration diagram of FIG. It is a thing. Therefore, in this embodiment, it switches to the cycle which compresses and discharges a refrigerant | coolant with the 2nd compressor 21 (2nd compression mechanism 21a) at the time of heating operation mode. Other configurations are the same as those of the sixth embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 37 (a) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 37 (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a, 51a, and 52a, and the first and second electric four-way valves 31 and 32 are operated. While switching to the circuit indicated by the solid line arrow, the high pressure side electric expansion valve 19a is brought into the throttle state.

  Thereby, as shown by the solid line arrow in FIG. 37, the first compressor 11 (→ the first electric four-way valve 31) → the outdoor heat exchanger 41 → the high-pressure side electric expansion valve 19a → the upstream branch section 22 (→ The refrigerant circulates in the order of the second check valve 16 b) → the nozzle portion 13 a of the ejector 13 → the outflow side heat exchanger 52 (→ the first electric four-way valve 31) → the first compressor 11, and the upstream branch portion 22. → Fixed throttle 18 → Use side heat exchanger 51 (→ second electric four-way valve 32) → Low pressure side refrigerant flow path 36b of the internal heat exchanger 36 → Second compressor 21 (→ second electric four-way valve 32) A cycle in which the refrigerant circulates in the order of the refrigerant suction port 13 b of the ejector 13, the outflow side heat exchanger 52, and the first compressor 11.

  That is, in the cooling operation mode of the present embodiment, a cycle exactly the same as that of the eighteenth embodiment is configured, and operates as shown in the Mollier diagram of FIG. The operation in the cooling operation mode is the same as the operation in the cooling operation mode of the eighteenth embodiment (FIG. 33 (a)). Therefore, in the cooling operation mode of this embodiment, the same effect as that of the cooling operation mode of the eighteenth embodiment can be obtained.

  Next, in the heating operation mode, the control device operates the second electric motor 21b and the blower fans 41a, 51a, and 52a, and switches the first and second electric four-way valves 31 and 32 to circuits indicated by broken line arrows, The high pressure side electric expansion valve 19a is brought into a throttled state, and the first electric motor 11b is stopped.

  As a result, as indicated by the broken line arrow in FIG. 36, the second compressor 21 (→ second electric four-way valve 32) → the use side heat exchanger 51 → the fixed throttle 18 → the upstream branch section 22 → the high pressure side electric type. Expansion valve 19a → outdoor heat exchanger 41 (→ first electric four-way valve 31) → outflow side heat exchanger 52 (→ ejector 13 → second electric four-way valve 32) → low-pressure side refrigerant flow of internal heat exchanger 36 A cycle in which the refrigerant circulates in the order of the path 36b → the second compressor 21 is configured.

Accordingly, the refrigerant compressed by the second compressor 21 (l ₃₇ point in FIG. 37 (b)) flows into the use-side heat exchanger 51 via the second electric four-way valve 32, and the blower fan 51a. The heat is exchanged with the air in the first storage box blown from the heat to dissipate heat (from ₃₇ points to ₃₇ points). Thereby, the air in the first storage is heated.

The refrigerant flowing out from the use side heat exchanger 51 flows into the internal heat exchanger 36 (fixed throttle 18), exchanges heat with the second compressor 21 suction refrigerant flowing through the low pressure side refrigerant flow path 36b, and the enthalpy thereof. (N ₃₇ points → n ′ ₃₇ points). Along with this, the enthalpy of the refrigerant sucked by the second compressor 21 increases (m ₃₇ points → m ′ ₃₇ points). Other operations are the same as in the sixth embodiment.

  Therefore, in the heating operation mode of the present embodiment, the refrigerant discharged from the second compressor 21 is radiated by the use side heat exchanger 51, and the radiated refrigerant is decompressed and expanded by the fixed throttle 18 and the high pressure side electric expansion valve 19a. Then, a refrigerant cycle in which the refrigerant expanded under reduced pressure is evaporated in the outdoor heat exchanger 41 and the outflow side heat exchanger 52 and the evaporated refrigerant is pressurized again in the second compressor 21 is configured.

  Thereby, the air in the first storage can be heated by the use side heat exchanger 51, and the air in the second storage can be cooled by the outflow side heat exchanger 52. Furthermore, in the heating operation mode of the present embodiment, not only the same effects as in the heating operation mode of the sixth embodiment can be obtained, but also in the heating operation mode by the action of the internal heat exchanger 36, the eighth embodiment. The COP improvement effect equivalent to (I) can be obtained.

(21st Embodiment)
In the ejector refrigeration cycle 700 of this embodiment, an internal heat exchanger 36 similar to that of the eighteenth embodiment is added to the ejector refrigeration cycle 200 of the seventh embodiment, as shown in the overall configuration diagram of FIG. It is a thing.

  Therefore, in this embodiment, it switches to the cycle which compresses and discharges a refrigerant | coolant with the 2nd compressor 21 (2nd compression mechanism 21a) at the time of heating operation mode. Further, in the ejector refrigeration cycle 700 of the present embodiment, the air in the second storage is neither heated nor cooled during the heating operation mode. Other configurations are the same as those of the seventh embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 39 (a) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 39 (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a, 51a, and 52a, and the first and second electric four-way valves 31 and 32 are operated. While switching to the circuit indicated by the solid line arrow, the high pressure side electric expansion valve 19a is brought into the throttle state.

  Thereby, as shown by the solid line arrow in FIG. 38, the first compressor 11 (→ the first electric four-way valve 31) → the outdoor heat exchanger 41 → the high-pressure side electric expansion valve 19a → the upstream branch section 22 (→ The refrigerant circulates in the order of the second check valve 16b) → the nozzle part 13a of the ejector 13 (→ the first electric four-way valve 31) → the outflow side heat exchanger 52 → the first compressor 11, and the upstream side branch part 22 → Fixed throttle 18 → Use side heat exchanger 51 (→ second electric four-way valve 32) → Low pressure side refrigerant flow path 36b of the internal heat exchanger 36 → Second compressor 21 (→ second electric four-way valve 32) → A refrigerant suction port 13b of the ejector 13 (→ first electric four-way valve 31) → outflow side heat exchanger 52 → first compressor 11 is cycled in this order.

  That is, in the cooling operation mode of the present embodiment, a cycle exactly the same as that of the eighteenth embodiment is configured and operates as shown in the Mollier diagram of FIG. The operation in the cooling operation mode is the same as the operation in the cooling operation mode of the eighteenth embodiment (FIG. 33 (a)). Therefore, in the cooling operation mode of this embodiment, the same effect as that of the cooling operation mode of the eighteenth embodiment can be obtained.

  Next, in the heating operation mode, the control device operates the second electric motor 21b and the blower fans 41a, 51a, and 52a, and switches the first and second electric four-way valves 31 and 32 to circuits indicated by broken line arrows, The high pressure side electric expansion valve 19a is brought into a throttled state, and the first electric motor 11b is stopped.

  As a result, as indicated by the broken line arrow in FIG. 38, the second compressor 21 (→ second electric four-way valve 32) → the use side heat exchanger 51 → the fixed throttle 18 → the upstream branch portion 22 → the high pressure side electric type. Expansion valve 19a → outdoor heat exchanger 41 (→ first electric four-way valve 31 → ejector 13 → second electric four-way valve 32) → low pressure side refrigerant flow path 36b of internal heat exchanger 36 → second compressor 21 A cycle in which the refrigerant circulates in sequence.

Therefore, the refrigerant compressed by the second compressor 21 (l ₃₉ points in FIG. 39 (b)) via the second electrical four-way valve 32, flows into the use-side heat exchanger 51, the blower fan 51a The heat is exchanged with the air in the first storage box blown from the heat to dissipate heat (l ₃₉ points → n ₃₉ points). Thereby, the air in the first storage is heated.

The refrigerant flowing out from the use side heat exchanger 51 flows into the internal heat exchanger 36 (fixed throttle 18), exchanges heat with the second compressor 21 suction refrigerant flowing through the low pressure side refrigerant flow path 36b, and the enthalpy thereof. (N ₃₉ points → n ′ ₃₉ points). Along with this, the enthalpy of the refrigerant sucked by the second compressor 21 increases (m ₃₉ points → m ′ ₃₉ points). Other operations are the same as those in the seventh embodiment.

  Therefore, in the heating operation mode of the present embodiment, the refrigerant discharged from the second compressor 21 is radiated by the use side heat exchanger 51, and the radiated refrigerant is decompressed and expanded by the fixed throttle 18 and the high pressure side electric expansion valve 19a. Thus, a refrigerant cycle in which the decompressed and expanded refrigerant is evaporated in the outdoor heat exchanger 41 and the evaporated refrigerant is increased in pressure by the second compressor 21 is configured.

  Thereby, in the heating operation mode of the present embodiment, the air in the second storage can not be cooled or heated, but the air in the first storage can be heated by the use side heat exchanger 51. Furthermore, in the heating operation mode of the present embodiment, not only the same effect as the heating operation mode of the seventh embodiment can be obtained, but also in the heating operation mode by the action of the internal heat exchanger 36, the eighth embodiment. The COP improvement effect equivalent to (I) can be obtained.

(Twenty-second embodiment)
40 and 41, the ejector-type refrigeration cycle 800 of the present invention includes a first storage that can be switched between cold storage, a second storage that can perform only low-temperature storage, and a third storage that can perform only high-temperature storage. An example applied to the storage will be described. FIG. 40 is an overall configuration diagram of the ejector refrigeration cycle 800 of the present embodiment.

  As shown in FIG. 23, in the ejector refrigeration cycle 800 of the present embodiment, the upstream branching portion 22 is eliminated from the ejector refrigeration cycle 200 of the fourth embodiment, and the discharge refrigerant of the first compressor 11 is eliminated. The discharge side branching part 24 that branches the flow of the refrigerant and the heat dissipation heat exchanger 54 that radiates heat of one of the refrigerants branched at the discharge side branching part 24 are added, and the connection mode of each component is changed. Yes.

  The basic configuration of the discharge side branch portion 24 is the same as that of the upstream side branch portion 22. The refrigerant heat inlet 54 is connected to the refrigerant inlet / outlet of the discharge branch 24, and one refrigerant inlet / outlet of the first electric four-way valve 31 is connected to the other refrigerant inlet / outlet. . Furthermore, in this embodiment, the fixed throttle 18 is connected to one refrigerant inlet / outlet of the outdoor heat exchanger 41.

  The heat dissipation heat exchanger 54 exchanges heat between the refrigerant passing through the inside and the air in the third storage box circulated and blown by the blower fan 54a. The blower fan 54a is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the control device. Further, the outlet side of the heat exchanger for heat dissipation 54 is connected to the inlet side of the nozzle portion 13a of the ejector 13 via a high pressure side electric expansion valve 19a as high pressure side pressure reducing means.

  Therefore, the first electric four-way valve 31 of the present embodiment is provided between the one refrigerant outlet of the discharge side branch portion 24 and the outdoor heat exchanger 41 and the outlet side of the diffuser portion 13d of the ejector 13 and the outlet side heat exchanger. 52 between the refrigerant flow path (circuit indicated by the solid line arrow in FIG. 40) and the outlet side of the discharge side branching portion 24 and the outlet side of the diffuser portion 13d, and the outdoor heat exchanger. 41 and the refrigerant flow path (circuit indicated by the broken line arrow in FIG. 40) that connects the outlet side heat exchanger 52 and the inlet side at the same time are switched. Other configurations are the same as those of the fourth embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 41 (a) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 41 (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a, 51a, 52a and 54a, and the first and second electric four-way valves 31, 32 is switched to a circuit indicated by a solid arrow, and the high-pressure side temperature expansion valve 19a is in a throttled state.

  Thereby, as shown by the solid line arrow in FIG. 40, the first compressor 11 → the discharge side branching portion 24 → the heat exchanger for heat dissipation 54 → the high pressure side electric expansion valve 19a → the nozzle portion 13a of the ejector 13 (→ first The refrigerant circulates in the order of the electric four-way valve 31) → the outflow side heat exchanger 52 → the first compressor, and the discharge side branch section 24 (→ the first electric four-way valve 31) → the outdoor heat exchanger 41 → the fixed throttle. 18 → use side heat exchanger 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → refrigerant suction port 13b of the ejector 13 → outflow side heat exchanger 52 → A cycle in which the refrigerant circulates in the order of the first compressor is configured.

Therefore, (a ₄₁ point in FIG. 41 (a)) the refrigerant compressed in the first compressor 11 (first compression mechanism 11a) flows into the discharge side branch section 24, to the radiating heat exchanger 54 side The refrigerant flow that flows out is divided into the refrigerant flow that flows out to the outdoor heat exchanger 41 side via the first electric four-way valve 31.

  Here, in this embodiment, the flow rate ratio Gr1 / Gr2 between the refrigerant flow rate Gr1 flowing into the heat dissipation heat exchanger 54 side and the refrigerant flow rate Gr2 flowing into the outdoor heat exchanger 41 side exhibits a high COP as a whole cycle. The passage areas (pressure loss characteristics) of the respective refrigerant passages in the discharge side branching portion 24 are determined so that the optimum flow rate ratio can be obtained.

The refrigerant that has flowed into the heat radiating heat exchanger 54 exchanges heat with the air in the third storage box circulated from the blower fan 54a to dissipate heat (a ₄₁ points → b ₁₄₁ points). Thereby, the air in the third storage is heated. The refrigerant that has flowed out of the heat-dissipating heat exchanger 54 flows into the high-pressure side electric expansion valve 19a, and is decompressed and expanded in an isoenthalpy manner to become a gas-liquid two-phase intermediate pressure refrigerant (b1 ₄₁ point → b1 ′ ₄₁ points).

At this time, the valve opening degree of the high-pressure side electric expansion valve 19a, the first compressor 11 the degree of superheat of suction refrigerant ₍₄₁ points f) is adjusted to be predetermined value. The intermediate-pressure refrigerant that has flowed out of the high-pressure side electric expansion valve 19a is decompressed and expanded in an isentropic manner at the nozzle portion 13a (b1 ′ ₄₁ points → c ₄₁ points).

Then, the refrigerant injected from the nozzle portion 13a and the suction refrigerant sucked from the refrigerant suction port 13b are mixed in the mixing portion 13c of the ejector 13 (c ₄₁ point → d ₄₁ point, j ₄₁ point → d ₄₁ point), are boosted by the diffuser part 13d (d ₄₁ points → e ₄₁ points).

The refrigerant flowing out of the diffuser section 13d flows into the outflow side heat exchanger 52 via the first electric four-way valve 31, and absorbs heat from the air in the second storage chamber circulated by the blower fan 52a to evaporate. (E ₄₁ points → f ₄₁ points). Thereby, the air in the second storage is cooled. Refrigerant flowing out from the outflow-side heat exchanger 52 is sucked into the first compressor 11 again is compressed (f ₄₁ points → a _41-point).

On the other hand, the refrigerant that has flowed into the outdoor heat exchanger 41 from the discharge side branching section 24 exchanges heat with the outside air (outside air) blown from the blower fan 41a to dissipate heat and condense (a ₄₁ points → b 2 ₄₁ point). The refrigerant that has flowed out of the outdoor heat exchanger 41 is further decompressed and expanded in an isoenthalpy manner by the fixed throttle 18 to reduce its pressure (b2 ₄₁ point → h ₄₁ point).

Decompressed and expanded refrigerant at a fixed throttle 18, and flows into the use-side heat exchanger 51, the blower fan 51a by such refrigerant is evaporated by absorbing heat from the first storage-compartment air circulated blown (h ₄₁ points → i ₄₁ point). Thereby, the air in the first storage is cooled. Other operations are the same as those in the fourth embodiment.

  Next, in the heating operation mode, the control device operates the first electric motor 11b and the blower fans 41a, 51a, 52a, and 54a, and the first and second electric four-way valves 31 and 32 are changed to circuits indicated by broken line arrows. The high pressure side temperature type expansion valve 19a is fully opened, and the second electric motor 21b is stopped.

  As a result, as indicated by the broken line arrow in FIG. 40, the first compressor 11 → the discharge side branching section 24 → the heat dissipating heat exchanger 54 (→ the high pressure side electric expansion valve 19a → the ejector 13 → the second electric four way valve 32) → second compressor 21 (→ second electric four-way valve 32) → use side heat exchanger 51 → fixed throttle 18 → outdoor heat exchanger 41 (→ first electric four-way valve 31) → outflow side heat exchange A cycle in which the refrigerant circulates in the order of the vessel 52 → the first compressor and the refrigerant flows in the order of the discharge side branch portion 24 → the first electric four-way valve 31 → the ejector 13 → the diffuser portion 13d is configured.

Therefore, (k ₄₁ points in FIG. 41 (b)) the refrigerant compressed in the first compressor 11 through the discharge-side branch portion 24, radiates heat by radiation heat exchanger 54 (k ₄₁ points → k1 ₄₁ points). Thereby, the air in the third storage is heated.

  The refrigerant radiated by the heat radiating heat exchanger 54 flows into the nozzle portion 13a of the ejector 13 through the high-pressure side electric expansion valve 19a. In the heating operation mode, since the high pressure side electric expansion valve 19a is fully opened, the refrigerant flowing through the high pressure side electric expansion valve 19a is not decompressed and expanded by the high pressure side electric expansion valve 19a. It flows into the ejector 13.

  Here, in the heating operation mode, the refrigerant compressed by the first compressor 11 also enters the ejector 13 from the diffuser portion 13d of the ejector 13 via the discharge side branch portion 24 and the first electric four-way valve 31. Inflow. Furthermore, there is almost no pressure difference between the pressure of the refrigerant flowing into the ejector 13 from the nozzle portion 13a and the pressure of the refrigerant flowing into the ejector 13 from the diffuser portion 13d.

For this reason, the refrigerant flowing into the ejector 13 from the nozzle portion 13a joins the refrigerant flowing into the ejector 13 from the diffuser portion 13d without being decompressed and expanded by the nozzle portion 13a (k1 ₄₁ point → k ′ ₄₁ Point, k ₄₁ points → k _'41 points). The refrigerant merged in the ejector 13 is slightly depressurized when passing through the ejector 13 (k ′ ₄₁ point → m ₄₁ point), and the use side heat exchanger 51 is passed through the second electric four-way valve 32. Flow into.

Refrigerant flowing into the utilization-side heat exchanger 51, and the replacement air heat first storage chamber which is circulated blown from the blower fan 51a is condensed by releasing heat (m ₄₁ points → n ₄₁ points). Thereby, the air in the first storage is heated. The refrigerant radiated by the use side heat exchanger 51 flows into the fixed throttle 18 and is decompressed and expanded in an enthalpy manner (n ₄₁ points → o ₄₁ points), flows into the outdoor heat exchanger 41, and blower fan 41a. It absorbs heat from the outside-compartment air (outside air) that has been blown from the (o ₄₁ points → o _'41 points).

The refrigerant that has flowed out of the outdoor heat exchanger 41 flows into the outflow side heat exchanger 52 via the first electric four-way valve 31, and further absorbs heat from the air in the second storage chamber that is circulated and blown by the blower fan 52a. And evaporate (o '41 _points- > p ₄₁ points). Thereby, the air in the second storage is cooled. Refrigerant flowing out from the outflow-side heat exchanger 52 is sucked into the first compressor 11, it is compressed again (p ₄₁ points → k ₄₁ points). Other operations are the same as those in the fourth embodiment.

  Therefore, when the ejector-type refrigeration cycle 800 of this embodiment is operated, in the cooling operation mode, the heat-dissipating heat exchanger 54 and the outdoor heat exchanger 41 function as heat radiators, and the use-side heat exchanger 51 and the outflow-side heat are operated. An ejector-type refrigeration cycle in which the exchanger 52 functions as an evaporator is configured.

  Thereby, the air in the first storage can be cooled by the use side heat exchanger 51, the air in the second storage can be cooled by the outflow side heat exchanger 52, and further, the air can be cooled by the heat exchanger 54 for heat radiation. 3 The air in the storage can be heated.

  In the heating operation mode, the refrigerant discharged from the first compressor 11 is radiated by the heat-dissipating heat exchanger 54 and the use-side heat exchanger 51, and the radiated refrigerant is decompressed and expanded by the fixed throttle 18, and is decompressed and expanded. Is re-evaporated by the outdoor heat exchanger 41 and the outflow side heat exchanger 52, and a refrigeration cycle is formed in which the first refrigerant 11 pressurizes the evaporated refrigerant again.

  As a result, the air in the first storage can be heated by the use side heat exchanger 51, the air in the second storage can be cooled by the outflow side heat exchanger 52, and further, the air can be cooled by the heat exchanger for heat dissipation 54. 3 The air in the storage can be heated.

  Further, in the ejector refrigeration cycle 800 of the present embodiment, not only can the same effects as in the fourth embodiment be obtained in each operation mode, but also the outdoor heat exchanger 41, the use side heat exchanger 51, the outflow side. The heat exchange performance of the heat exchanger 52 and the heat dissipation heat exchanger 54 can be changed independently. Therefore, for example, since the heat dissipation performance of the outdoor heat exchanger 41 and the heat absorption performance of the use-side heat exchanger 51 can be easily matched, the cycle operation can be further stabilized.

(23rd Embodiment)
In the present embodiment, the ejector-type refrigeration is changed to a cold storage container in which the arrangement of the outflow side heat exchanger 52 is changed with respect to the twenty-second embodiment so that both the first and second storage containers can be switched to cold storage. An example in which the cycle 800 is applied will be described. Specifically, as shown in the overall configuration diagram of FIG. 42, the outflow side heat exchanger 52 of the present embodiment includes the diffuser portion 13 d outlet of the ejector 13 and one refrigerant inlet and outlet of the first electric four-way valve 31. It is arranged between.

  Therefore, the first electric four-way valve 31 of the present embodiment is provided between the one refrigerant outlet of the discharge side branching portion 24 and the outdoor heat exchanger 41, and the outlet side heat exchanger 52 and the first compressor 11 intake port. Between the refrigerant flow path (circuit indicated by the solid line arrow in FIG. 42) and the one refrigerant outlet of the discharge side branching section 24 and the outflow side heat exchanger 52, and the outdoor heat exchanger 41. And a refrigerant flow path (circuit shown by a broken line arrow in FIG. 42) that connects the first compressor 11 and the suction port side at the same time. Other configurations are the same as those in the twenty-second embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 43 (a) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 43 (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a, 51a, 52a and 54a, and the first and second electric four-way valves 31, 32 is switched to a circuit indicated by a solid arrow, and the high-pressure side electric expansion valve 19a is brought into a throttled state.

  Thereby, as shown by the solid line arrow in FIG. 42, the first compressor 11 → the discharge side branching portion 24 → the heat exchanger for heat dissipation 54 → the high pressure side electric expansion valve 19a → the nozzle portion 13a of the ejector 13 → the outflow side heat. While the refrigerant circulates in the order of the exchanger 52 (→ first electric four-way valve 31) → first compressor, the discharge side branch section 24 (→ first electric four-way valve 31) → outdoor heat exchanger 41 → fixed throttle 18 → use side heat exchanger 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → refrigerant suction port 13b of the ejector 13 → outflow side heat exchanger 52 → A cycle in which the refrigerant circulates in the order of the first compressor is configured.

  That is, in the cooling operation mode of the present embodiment, a cycle exactly the same as that of the cooling operation mode of the twenty-second embodiment is configured, and operates as shown in the Mollier diagram of FIG. The operation in the cooling operation mode is the same as the operation in the cooling operation mode of the twenty-second embodiment (FIG. 41 (a)). Therefore, in the cooling operation mode of the present embodiment, the same effect as that of the cooling operation mode of the twenty-second embodiment can be obtained.

  Next, in the heating operation mode, the control device operates the first electric motor 11b and the blower fans 41a, 51a, 52a, and 54a, and the first and second electric four-way valves 31 and 32 are changed to circuits indicated by broken line arrows. The high pressure side temperature type expansion valve 19a is fully opened, and the second electric motor 21b is stopped.

  Thereby, as indicated by the broken line arrow in FIG. 42, the first compressor 11 → the discharge side branching portion 24 → the heat exchanger 54 for heat dissipation (→ the high pressure side electric expansion valve 19a → the ejector 13 → the second electric four way valve 32) → use side heat exchanger 51 → fixed throttle 18 → outdoor heat exchanger 41 (→ first electric four-way valve 31) → first compressor, and a cycle in which the refrigerant circulates is configured and the discharge side branch A cycle is formed in which the refrigerant flows in the order of section 24 (→ first electric four-way valve 31) → outflow side heat exchanger 52 → ejector 13 →.

Therefore, of the refrigerant compressed (k ₄₃ points in FIG. 43 (b)) at the first compressor 11, refrigerant flowing into the heat dissipation heat exchanger 54 side from the discharge side branch portion 24, the heat exchanger for heat radiation The heat is dissipated by the vessel 54 (k ₄₃ points → k1 ₄₃ points). Thereby, the air in the third storage is heated. The refrigerant radiated by the heat radiating heat exchanger 54 flows into the nozzle portion 13a of the ejector 13 through the high-pressure side electric expansion valve 19a.

Further, the refrigerant that has flowed into the outflow side heat exchanger 52 via the first electric four-way valve 31 from the discharge side branch section 24 radiates heat in the outflow side heat exchanger 52 (k ₄₃ points → k2 ₄₃ points). ). Thereby, the air in the second storage is heated. The refrigerant radiated by the outflow side heat exchanger 52 flows into the diffuser portion 13d of the ejector 13.

Then, the refrigerant flowing into the ejector 13 from the nozzle portion 13a and the refrigerant flowing into the ejector 13 from the diffuser portion 13d merge in the ejector 13 (k1 ₄₃ points → k ′ ₄₃ points) as in the twenty-second embodiment. , k2 ₄₃ points → k _'43 points).

The refrigerant merged in the ejector 13 is slightly depressurized when passing through the ejector 13 (k ′ ₄₃ points → m ₄₃ points) and flows into the use side heat exchanger 51. The refrigerant that has flowed into the use side heat exchanger 51 and the refrigerant that has flowed into the use side heat exchanger 51 exchange heat with the inside air circulated from the blower fan 51a to dissipate heat and condense (m ₄₃ points). → n ₄₃ points). Thereby, the air in the first storage is heated.

The refrigerant radiated by the use side heat exchanger 51 flows into the fixed throttle 18 and is decompressed and expanded in an enthalpy manner (n ₄₃ points → o ₄₃ points), flows into the outdoor heat exchanger 41, and blower fan 41a. Heat is absorbed from outside air (outside air) blown from (o ₄₃ points → p ₄₃ points). The refrigerant flowing out of the outdoor heat exchanger 41 is sucked into the first compressor 11 through the first electric four-way valve 31. Other operations are the same as those in the twenty-second embodiment.

  Therefore, in the heating operation mode of the present embodiment, the refrigerant discharged from the first compressor 11 is radiated by the use side heat exchanger 51, the outflow side heat exchanger 52, and the heat dissipation heat exchanger 54, and the radiated refrigerant is fixed to the fixed throttle. The refrigerant is decompressed and expanded at 18, the decompressed and expanded refrigerant is evaporated by the outdoor heat exchanger 41, and the evaporated refrigerant is again pressurized by the first compressor 11.

  Thereby, the air in the first storage can be heated by the use side heat exchanger 51, the air in the second storage can be heated by the outflow side heat exchanger 52, and further, the air can be heated by the heat exchanger 54 for heat dissipation. 3 The air in the storage can be heated. Furthermore, the cycle can be stably operated as in (C) of the first embodiment.

(24th Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 44, the connection mode of each component device is changed with respect to the ejector refrigeration cycle 800 of the 22nd embodiment, and the second compressor 21 is changed in the heating operation mode. An example in which the cycle is switched to a cycle in which the refrigerant is compressed and discharged by the (second compression mechanism 21a) will be described. In the ejector refrigeration cycle 800 of the present embodiment, the air in the third storage is neither heated nor cooled during the heating operation mode.

  Specifically, the outflow side heat exchanger 52 of the present embodiment is disposed between the diffuser portion 13 d outlet of the ejector 13 and one refrigerant inflow / outlet of the first electric four-way valve 31.

  Further, the first electric four-way valve 31 is provided between one refrigerant outlet of the discharge side branching section 24 and the outdoor heat exchanger 41 and between the outflow side heat exchanger 52 and the first compressor 11 suction side. At the same time, between the outdoor heat exchanger 41 and the outflow side heat exchanger 52 and between the discharge side and the suction side of the first compressor 11. Are switched to the refrigerant flow path (circuit indicated by the broken line arrow in FIG. 44).

  Further, the second electric four-way valve 32 is provided between the use-side heat exchanger 51 and the second compressor 21 suction port side and between the second compressor 21 discharge port side and the refrigerant suction port 13b side of the ejector 13 simultaneously. The refrigerant flow path (circuit indicated by the solid arrow in FIG. 44), the second compressor 21 discharge side and the use side heat exchanger 51, the refrigerant suction port 13b side, and the second compressor 21 suction port side. Are switched to the refrigerant flow paths (circuits indicated by broken line arrows in FIG. 44). Other configurations are the same as those in the twenty-second embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 45 (a) is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 45 (b) is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a, 51a, 52a and 54a, and the first and second electric four-way valves 31, 32 is switched to a circuit indicated by a solid arrow, and the high-pressure side electric expansion valve 19a is brought into a throttled state.

  As a result, as indicated by the solid line arrow in FIG. 44, the first compressor 11 → the discharge side branch 24 → the heat exchanger 54 for heat dissipation → the high pressure side electric expansion valve 19a → the nozzle part 13a of the ejector 13 → the outflow side heat. While the refrigerant circulates in the order of the exchanger 52 (→ first electric four-way valve 31) → first compressor, the discharge side branch section 24 (→ first electric four-way valve 31) → outdoor heat exchanger 41 → fixed throttle 18 → use side heat exchanger 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → refrigerant suction port 13b of the ejector 13 → outflow side heat exchanger 52 ( → First electric four-way valve 31) A cycle in which the refrigerant circulates in the order of the first compressor.

  That is, in the cooling operation mode of the present embodiment, a cycle that is exactly the same as that of the cooling operation mode of the twenty-second embodiment is configured, and operates as shown in the Mollier diagram of FIG. The operation in the cooling operation mode is the same as the operation in the cooling operation mode of the twenty-second embodiment (FIG. 41 (a)). Therefore, in the cooling operation mode of the present embodiment, the same effect as that of the cooling operation mode of the twenty-second embodiment can be obtained.

  Next, in the heating operation mode, the control device operates the second electric motor 21b and the blower fans 41a, 51a, and 52a, and switches the first and second electric four-way valves 31 and 32 to circuits indicated by broken line arrows, The high pressure side temperature type expansion valve 19a is fully closed, and the first electric motor 21b and the blower fan 54a are stopped.

  As a result, as indicated by the broken line arrow in FIG. 44, the second compressor 21 (→ second electric four-way valve 32) → the use side heat exchanger 51 → the fixed throttle 18 → the outdoor heat exchanger 41 (→ first electric The cycle in which the refrigerant circulates in the order of the four-way valve 31) → the outflow heat exchanger 52 (→ the ejector 13 → the second electric four-way valve 32) → the second compressor 21.

Accordingly, the refrigerant compressed by the second compressor 21 ( ₄₅ point in FIG. 45 (b)) flows into the use side heat exchanger 51 through the second electric four-way valve 32 and is blown by the blower fan 51a. Heat is exchanged with the circulating air in the first storage chamber to dissipate heat (l ₄₅ points → n ₄₅ points). Thereby, the air in the first storage is heated.

The refrigerant that has flowed out of the use-side heat exchanger 51 is decompressed and expanded in an enthalpy manner by the fixed throttle 18 (n ₄₅ points → o ₄₅ points) and flows into the outdoor heat exchanger 41 as in the twenty-second embodiment. The refrigerant flowing into the outdoor heat exchanger 41 absorbs heat from the outside air blown from the blower fan 41a (o ₄₅ points → o ′ ₄₅ points).

The refrigerant that has flowed out of the outdoor heat exchanger 41 flows into the outflow side heat exchanger 52 through the first electric four-way valve 31, and absorbs heat from the air in the second storage chamber that is circulated and blown by the blower fan 52a. Evaporates (o '45 _points- > p ₄₅ points). Thereby, the air in the second storage is cooled.

Refrigerant flowing out from the outflow-side heat exchanger 52 flows into the ejector 13 through the first electric four-way valve 31, slightly decompressed by (p ₄₅ points → m ₄₅ points when backflow through the ejector 13 ). At this time, in the heating operation mode, since the high-pressure side temperature type expansion valve 19a is fully closed, the refrigerant flowing into the ejector 13 flows out from the refrigerant suction port 13b of the ejector 13.

  The refrigerant flowing out from the refrigerant suction port 13b of the ejector 13 is sucked into the second compressor 21 via the second electric four-way valve 32 and compressed again. Other operations are the same as those in the twenty-second embodiment.

  Therefore, in the heating operation mode of the present embodiment, the refrigerant discharged from the second compressor 21 is radiated by the use-side heat exchanger 51, the radiated refrigerant is decompressed and expanded by the fixed throttle 18, and the decompressed and expanded refrigerant is subjected to outdoor heat. A refrigeration cycle is configured in which the refrigerant is evaporated by the exchanger 41 and the outflow side heat exchanger 52, and the evaporated refrigerant is pressurized again by the second compressor 21.

  Thereby, in the heating operation mode of the present embodiment, the air in the third storage chamber cannot be cooled or heated, but the function of the first compressor 11 in the 22nd embodiment is fulfilled by the second compressor 21. Thus, the use-side heat exchanger 51 can heat the air in the first storage compartment, and the outflow-side heat exchanger 52 can cool the air in the second storage compartment.

(25th Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 46, the connection mode of each component device is changed with respect to the ejector refrigeration cycle 800 of the twenty-second embodiment, and the second compressor 21 ( An example in which the second compression mechanism 21a) is configured to switch to a cycle in which the refrigerant is compressed and discharged will be described. In the ejector refrigeration cycle 800 of the present embodiment, the air in the second and third storage compartments is neither heated nor cooled during the heating operation mode.

  Specifically, the first electric four-way valve 31 of the present embodiment is provided between the one refrigerant outlet of the discharge side branching portion 24 and the outdoor heat exchanger 41 and the outlet side and the outlet side of the diffuser portion 13d of the ejector 13. A refrigerant flow path (a circuit indicated by a solid line arrow in FIG. 46) that connects the heat exchanger 52 at the same time, between the outdoor heat exchanger 41 and the diffuser portion 13d outlet side of the ejector 13, and the first compressor 11 discharge The refrigerant flow path (circuit indicated by a broken line arrow in FIG. 46) that connects the outlet side and the suction port side at the same time is switched.

  Further, the second electric four-way valve 32 is provided between the use-side heat exchanger 51 and the second compressor 21 suction port side and between the second compressor 21 discharge port side and the refrigerant suction port 13b side of the ejector 13 simultaneously. The refrigerant flow path (circuit shown by the solid line arrow in FIG. 46), the second compressor 21 discharge side and the use side heat exchanger 51, the refrigerant suction port 13b side, and the second compressor 21 suction port side. Are switched to a refrigerant flow path (circuit indicated by a broken line arrow in FIG. 46). Other configurations are the same as those in the twenty-second embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 47A is a Mollier diagram showing the state of the refrigerant in the cooling operation mode, and FIG. 47B is a Mollier diagram showing the state of the refrigerant in the heating operation mode.

  First, in the cooling operation mode of the present embodiment, the control device operates the first and second electric motors 11b and 21b and the blower fans 41a, 51a, 52a and 54a, and the first and second electric four-way valves 31, 32 is switched to a circuit indicated by a solid arrow, and the high-pressure side electric expansion valve 19a is brought into a throttled state.

  As a result, as indicated by the solid line arrow in FIG. 46, the first compressor 11 → the discharge side branch portion 24 → the heat exchanger for heat dissipation 54 → the high pressure side electric expansion valve 19a → the nozzle portion 13a of the ejector 13 (→ first The refrigerant circulates in the order of the electric four-way valve 31) → the outflow side heat exchanger 52 → the first compressor, and the discharge side branch section 24 (→ the first electric four-way valve 31) → the outdoor heat exchanger 41 → the fixed throttle. 18 → use side heat exchanger 51 (→ second electric four-way valve 32) → second compressor 21 (→ second electric four-way valve 32) → refrigerant suction port 13b of the ejector 13 (→ first electric four-way valve) 31) → the outflow side heat exchanger 52 → the cycle in which the refrigerant circulates in the order of the first compressor.

  That is, in the cooling operation mode of the present embodiment, a cycle exactly the same as that of the cooling operation mode of the twenty-second embodiment is configured and operates as shown in the Mollier diagram of FIG. The operation in the cooling operation mode is the same as the operation in the cooling operation mode of the twenty-second embodiment (FIG. 41 (a)). Therefore, in the cooling operation mode of the present embodiment, the same effect as that of the cooling operation mode of the twenty-second embodiment can be obtained.

  Next, in the heating operation mode, the control device operates the second electric motor 21b and the blower fans 41a and 51a to switch the first and second electric four-way valves 31 and 32 to the circuit indicated by the broken-line arrow, The temperature type expansion valve 19a is fully closed, and the first electric motor 21b, the blower fan, 52a and 54a are stopped.

  46, the second compressor 21 (→ second electric four-way valve 32) → the use side heat exchanger 51 → the fixed throttle 18 → the outdoor heat exchanger 41 (first electric type). A cycle in which the refrigerant circulates in the order of the four-way valve 31 → the ejector 13 → the second electric four-way valve 32) → the second compressor 21.

Therefore, the refrigerant compressed by the second compressor 21 (l ₄₇ points in FIG. 47 (b)) flows into the use-side heat exchanger 51 via a second electric four-way valve 32, the blower fan 51a Heat is exchanged with the circulating air in the first storage chamber to dissipate heat (l ₄₇ points → n ₄₇ points). Thereby, the air in the first storage is heated.

The refrigerant that has flowed out of the use side heat exchanger 51 is decompressed and expanded in an enthalpy manner at the fixed restrictor 18 (n ₄₇ points → o ₄₇ points) and flows into the outdoor heat exchanger 41 as in the twenty-second embodiment. The refrigerant flowing into the outdoor heat exchanger 41 absorbs heat from the outside air blown from the blower fan 41a (o ₄₇ points → p ₄₇ points).

The refrigerant flowing out of the outdoor heat exchanger 41 flows into the ejector 13 via the first electric four-way valve 31, and is slightly reduced in pressure when flowing back in the ejector 13 (p ₄₇ points → m ₄₇ points). ). Other operations are the same as those in the twenty-second embodiment.

  Therefore, in the heating operation mode of the present embodiment, the refrigerant discharged from the second compressor 21 is radiated by the use-side heat exchanger 51, the radiated refrigerant is decompressed and expanded by the fixed throttle 18, and the decompressed and expanded refrigerant is subjected to outdoor heat. A refrigeration cycle is configured in which the refrigerant is evaporated by the exchanger 41 and the evaporated refrigerant is again pressurized by the second compressor 21.

  Thus, in the heating operation mode of the present embodiment, the air in the second and third storages cannot be cooled or heated, but the function of the first compressor 11 in the 22nd embodiment is the same as that of the second compressor 21. As a result, the use-side heat exchanger 51 can heat the air in the first storage.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows.

  (1) In the above-described embodiment, the refrigerant flow constituting the vapor compression refrigeration cycle that switches to the refrigerant flow path constituting the ejector refrigeration cycle during the cooling operation mode and boosts the refrigerant in multiple stages during the heating operation mode. The example of switching to the road, that is, the cooling operation mode corresponds to one operation mode described in the claims and the heating operation mode corresponds to the other operation mode described in the claims, You may make it switch to a reverse structure.

  That is, during the cooling operation mode, switching to the refrigerant flow path constituting the refrigeration cycle for boosting the refrigerant in multiple stages, and during the heating operation mode, switching to the refrigerant flow path constituting the ejector refrigeration cycle, that is, the heating operation mode is patented. The cooling operation mode may correspond to one operation mode described in the claims, and the cooling operation mode may correspond to the other operation mode described in the claims.

  As a result, the cycle can be stably operated while exhibiting a high COP in the heating operation mode, so that the cold storage room used in the environment where the outside air as the heat absorption source is at a very low temperature as the heat sink. Etc., it is extremely effective.

  (2) In the above-described embodiment, the first and second compressors 11 and 21 have been described as adopting separate compressors. However, the first and second compression mechanisms 11a and 21a and The first and second electric motors 11b and 21b may be configured integrally.

  For example, the first and second compression mechanisms 11a and 21a and the first and second electric motors 11b and 21b may be accommodated in the same housing and integrally configured. In this case, the rotation shafts of the first and second compression mechanisms 11a and 21a may be shared, and both compression mechanisms may be driven by a driving force supplied from a common drive source.

  Thereby, the 1st, 2nd compression mechanism 11a, 21a can be reduced in size, and size reduction as the whole ejector-type refrigerating cycle can be achieved.

  (3) In the above-described embodiment, the example in which the electric compressor is adopted as the first and second compressors 11 and 21 has been described. However, the format of the first and second compressors 11 and 21 is not limited to this. .

  For example, you may employ | adopt the variable capacity type compressor which can adjust a refrigerant | coolant discharge capability with the change of discharge capacity | capacitance by using an engine etc. as a drive source. In this case, the discharge capacity changing means becomes the discharge capacity changing means. Moreover, you may use the fixed capacity type compressor which adjusts a refrigerant | coolant discharge capability by changing the connection with a drive source intermittently by the interruption of an electromagnetic clutch. In this case, the electromagnetic clutch becomes the discharge capacity changing means.

  Further, the first and second compressors 11 and 21 may employ the same type of compression mechanism or different types of compression mechanisms.

  (4) In the above-described embodiment, the fixed ejector 13 in which the throttle passage area of the nozzle portion 13a is fixed is adopted as the ejector 13. However, the variable ejector configured to be able to change the throttle passage area of the nozzle portion. May be adopted.

  Moreover, although the above-mentioned embodiment demonstrated the example which employ | adopted the electric expansion valve as a high pressure side pressure reduction means and a low pressure side pressure reduction means, these pressure reduction means are not limited to an electric expansion valve. For example, a configuration in which a fixed throttle and a solenoid valve (open / close valve) are combined may be employed. Furthermore, although the example which employ | adopted the fixed throttle as a refrigerant pressure reduction means was demonstrated, you may employ | adopt a variable throttle mechanism as a refrigerant pressure reduction means.

  Further, as the separation refrigerant pressure reducing means of the first to third embodiments, a configuration in which an electric expansion valve or a fixed throttle and an electromagnetic valve (open / close valve) are combined is adopted, and the first check valve 16a is eliminated. Also good. In this case, the operation of the electric expansion valve or electromagnetic valve (open / close valve) may be controlled so as to block the refrigerant passage from the accumulator 14 to the first three-way joint 17a in the heating operation mode.

  Further, as the refrigerant pressure reducing means, the high pressure side pressure reducing means, the low pressure side pressure reducing means, and the separated refrigerant pressure reducing means, an expander that expands and decompresses the refrigerant and converts the pressure energy of the refrigerant into mechanical energy and outputs it is adopted. May be.

  As such an expander, specifically, a volume type compression means such as a scroll type, a vane type, or a rolling piston type can be employed. Then, by flowing the refrigerant so that it flows backward with respect to the refrigerant flow when the positive displacement compression means is used as the compression means, mechanical energy can be output while the refrigerant is volume-expanded and depressurized.

  (5) In the above-described embodiment, an example in which a normal chlorofluorocarbon refrigerant is employed as the refrigerant has been described. However, the type of refrigerant is not limited to this. For example, hydrocarbon refrigerant, carbon dioxide, etc. may be used. Furthermore, the ejector refrigeration cycle of the present invention may be configured as a supercritical refrigeration cycle in which the high-pressure side refrigerant pressure exceeds the critical pressure of the refrigerant.

  Further, when the ejector refrigeration cycles 100 to 800 are supercritical refrigeration cycles, the high-pressure side pressure reducing means may be eliminated. Thereby, since the pressure reduction amount in the nozzle part 13a of the ejector 13 can be increased, the difference (recovered energy amount) between the enthalpy of the nozzle part 19a inlet side refrigerant and the enthalpy of the nozzle part 19a outlet side refrigerant is also increased. COP can be further improved.

  Furthermore, when configuring a supercritical refrigeration cycle, as a high pressure side decompression means, a pressure that is adjusted to a target high pressure that is determined so that the COP becomes substantially maximum based on the outlet side refrigerant temperature of the heat exchanger that functions as a radiator. A control valve may be employed.

  As such a pressure control valve, specifically, it has a temperature sensing part provided on the heat exchanger outlet side that functions as a radiator, and a heat exchanger outlet that functions as a radiator inside the temperature sensing part. It is possible to adopt a configuration in which a pressure corresponding to the temperature of the side refrigerant is generated, and the valve opening is adjusted by a mechanical mechanism by a balance between the internal pressure of the temperature sensing unit and the refrigerant pressure on the outlet side of the heat exchanger functioning as a radiator.

  (6) In each of the above-described embodiments, the example in which the first and second electric four-way valves 31, 32, the electric three-way valve 33, and the like are employed as the refrigerant flow path switching means has been described. Is not limited to this.

  For example, as shown in FIG. 48 (a), two electric three-way valves 31a may be combined instead of the first electric four-way valve 31, or as shown in FIG. 48 (b), You may comprise combining the four on-off valves (electromagnetic valve) 31b. As shown in FIG. 49, three open / close valves (electromagnetic valves) 33b may be combined instead of the electric three-way valve 33.

  (7) In the above embodiment, the refrigerant flow direction in the high-pressure side refrigerant flow path 35a of the internal heat exchanger 35 and the refrigerant flow direction in the low-pressure side refrigerant flow path 35b are not mentioned, but the refrigerant in the high-pressure side refrigerant flow path. The flow direction may be a parallel flow in which the refrigerant flow direction in the low-pressure side refrigerant flow path is the same direction, or the refrigerant flow direction in the high-pressure side refrigerant flow path is opposite to the refrigerant flow direction in the low-pressure side refrigerant flow path. It may be a flow.

  Further, in the cooling operation modes of the fourteenth to seventeenth and twenty-second to twenty-fifth embodiments, the outflow side heat exchanger 52 and the blower fan 52a are abolished, and the outflow is performed from the auxiliary heat exchanger 53 or the outdoor heat exchanger 41. Thus, an internal heat exchanger is employed that exchanges heat between the high-pressure refrigerant flowing into the fixed throttle 18 and the low-pressure refrigerant flowing out of the diffuser portion 13d of the ejector 13, that is, the low-pressure refrigerant sucked into the first compression means 21a. May be.

  (8) In each of the above-described embodiments, the example in which the ejector refrigeration cycle 100 to 800 of the present invention is applied to a cold storage is described, but the application of the present invention is not limited to this. For example, the ejector refrigeration cycle may be applied to an air conditioner, another stationary refrigeration cycle apparatus, a vehicle refrigeration cycle apparatus, or the like.

DESCRIPTION OF SYMBOLS 11, 21 1st, 2nd compressor 11a, 21a 1st, 2nd compression mechanism 11b, 21b 1st, 2nd electric motor 13 Ejector 13a Nozzle part 13b Refrigerant suction port 13d Diffuser part 14 Accumulator 22 Upstream branch part 23 Downstream branch portion 24 Discharge side branch portion 18 Fixed throttle 31, 32 First and second electric four-way valve 33 Electric three-way valve 41 Outdoor heat exchanger 51 Use side heat exchanger 52 Outflow side heat exchanger 53 Auxiliary heat exchange 54 Heat exchanger for heat dissipation

Claims (26)

First and second compression mechanisms (11a, 21a) for compressing and discharging the refrigerant;
An outdoor heat exchanger (41) for exchanging heat between the refrigerant and the outside air;
A use side heat exchanger (51) for exchanging heat between the refrigerant and the fluid to be heat exchanged;
The refrigerant sucked from the refrigerant suction port (13b) by the flow of the high-speed jet refrigerant jetted from the nozzle part (13a) for decompressing and expanding the refrigerant, and sucked from the jetted refrigerant and the refrigerant suction port (13b) An ejector (13) for increasing the pressure of the refrigerant mixed with the refrigerant at the diffuser section (13d);
Refrigerant decompression means (18) for decompressing and expanding the refrigerant;
A refrigerant passage in cooling operation mode for cooling the heat exchange target fluid, and refrigerant passage switching means (31, 32, 33) for switching the refrigerant passage in heating operation mode for heating the heat exchange target fluid. ,
The refrigerant flow switching means (31 to 33)
During one of the cooling operation mode and the heating operation mode, the refrigerant discharged from the first compression mechanism (11a) is supplied to one of the outdoor heat exchanger (41) and the use side heat exchanger (51). Heat is radiated by the heat exchanger, and the refrigerant radiated by the one heat exchanger is caused to flow into the nozzle portion (13a), and the outdoor heat exchanger (41) and the use side heat exchanger (51) Among them, the refrigerant evaporated in the other heat exchanger is sucked into the second compression mechanism (21a) and switched to the refrigerant flow path for discharging to the refrigerant suction port (13b) side,
During the other operation mode of the cooling operation mode and the heating operation mode, the refrigerant discharged from one of the first and second compression mechanisms (11a, 21a) is transferred to the other heat exchanger. The refrigerant that has radiated heat at the other heat exchanger and that has radiated heat at the other heat exchanger flows into the refrigerant pressure reducing means (18), and at the same time the refrigerant that has evaporated at the one heat exchanger is sucked into the one compression mechanism An ejector type refrigeration cycle characterized by switching to a flow path. A gas-liquid separator (14) for separating the gas-liquid refrigerant and causing the separated gas-phase refrigerant to flow out to the suction side of the first compression mechanism (11a);
Separation refrigerant decompression means (15) for decompressing and expanding the liquid refrigerant separated in the gas-liquid separator (14),
The refrigerant flow switching means (31 to 33)
In the one operation mode, the refrigerant flowing out of the diffuser section (13d) is sucked into the first compression mechanism (11a) through the gas-liquid separator (14), and is separated by the separated refrigerant pressure reducing means (15). 2. The ejector-type refrigeration cycle according to claim 1, wherein the refrigerant flow is switched to a refrigerant flow path for allowing the refrigerant expanded under reduced pressure to flow into the other heat exchanger. The one compression mechanism is a first compression mechanism (11a),
The refrigerant flow switching means (31 to 33)
In the other operation mode, the refrigerant decompressed and expanded by the refrigerant decompression means (18) is caused to flow into the one heat exchanger, and the refrigerant flowing out from the one heat exchanger is allowed to flow into the gas-liquid separator ( 14. The ejector refrigeration cycle according to claim 2, wherein the refrigerant flow path is switched to a refrigerant flow path to be sucked into the first compression mechanism (11 a) via 14). The one compression mechanism is a second compression mechanism (21a),
The refrigerant flow switching means (31 to 33)
In the other operation mode, the refrigerant decompressed and expanded by the refrigerant decompression means (18) is caused to flow into the one heat exchanger, and the refrigerant flowing out from the one heat exchanger is allowed to flow into the gas-liquid separator ( 14. The ejector refrigeration cycle according to claim 2, wherein the refrigerant flow path is switched to a refrigerant flow path bypassing 14) and sucked into the first compression mechanism (11 a). An upstream branching section (22) for branching the flow of the refrigerant flowing into the nozzle section (13a) and allowing the branched one refrigerant to flow out to the nozzle section (13a) side;
The refrigerant flow switching means (31, 32)
In the one operation mode, the other refrigerant branched at the upstream branch (22) is caused to flow into the refrigerant decompression means (18), and the refrigerant decompressed by the refrigerant decompression means (18) The refrigerant is caused to flow into the other heat exchanger, and further, the refrigerant flowed out of the diffuser portion (13d) is switched to a refrigerant flow path for sucking into the first compression mechanism (11a).
In the other operation mode, the refrigerant decompressed and expanded by the refrigerant decompression means (18) is switched to the refrigerant flow path for flowing into the one heat exchanger via the upstream branch section (22). The ejector-type refrigeration cycle according to claim 1.   The outflow side heat exchanger (52) that evaporates the refrigerant that flows out of the diffuser section (13d) and is sucked into the first compression mechanism (11a) in the one operation mode. 5. The ejector type refrigeration cycle according to 5. The one compression mechanism is a first compression mechanism (11a),
The refrigerant flow switching means (31, 32)
In the one operation mode, switching to the refrigerant flow path for evaporating the refrigerant flowing out of the diffuser part (14d) in the outflow side heat exchanger (52),
The ejector refrigeration according to claim 6, wherein, in the other operation mode, the refrigerant is switched to a refrigerant flow path for evaporating the refrigerant flowing out from the one heat exchanger in the outflow side heat exchanger (52). cycle. The one compression mechanism is a first compression mechanism (11a),
The refrigerant flow switching means (31, 32)
In the one operation mode, switching to the refrigerant flow path for evaporating the refrigerant flowing out of the diffuser part (14d) in the outflow side heat exchanger (52),
The ejector-type refrigeration according to claim 6, wherein, in the other operation mode, the refrigerant is switched to a refrigerant flow path that radiates the refrigerant discharged from the first compression mechanism (11a) in the outflow side heat exchanger (52). cycle. The one compression mechanism is a second compression mechanism (21a),
The refrigerant flow switching means (31, 32)
In the one operation mode, switching to the refrigerant flow path for evaporating the refrigerant flowing out of the diffuser part (14d) in the outflow side heat exchanger (52),
The ejector refrigeration according to claim 6, wherein, in the other operation mode, the refrigerant is switched to a refrigerant flow path for evaporating the refrigerant flowing out from the one heat exchanger in the outflow side heat exchanger (52). cycle.   Arranged between the upstream branching section (22) and the refrigerant pressure reducing means (18), in the one operation mode, the other refrigerant branched in the upstream branching section (22) is dissipated. The auxiliary heat exchanger (53) for evaporating the refrigerant decompressed and expanded by the refrigerant decompression means (18) in the other operation mode is provided. The ejector refrigeration cycle described.   An internal heat exchanger (35) for exchanging heat between the other refrigerant branched at the upstream branch (22) and the suction refrigerant in the second compression mechanism (21a) during the one operation mode; The ejector-type refrigeration cycle according to any one of claims 5 to 10, wherein   An internal heat exchanger (36) for exchanging heat between the refrigerant in the decompression expansion process in the refrigerant decompression means (18) and the suction refrigerant in the second compression mechanism (21a) during the one operation mode is characterized. The ejector type refrigeration cycle according to any one of claims 5 to 10. A downstream branch section (23) for branching the flow of the refrigerant flowing out from the diffuser section (13d),
An outflow side heat exchanger (52) for evaporating one refrigerant branched in the downstream branch section (23) during the one operation mode;
Low pressure side decompression means (19b) for decompressing and expanding the other refrigerant branched at the downstream side branch section (23) during the one operation mode;
The refrigerant flow switching means (31 to 33)
During the one operation mode, the refrigerant that has flowed out of the outflow side heat exchanger (52) is sucked into the first compression mechanism (11a), and the refrigerant that has been decompressed and expanded by the low pressure side decompression means (19b) is Switch to the refrigerant flow path to flow into the other heat exchanger,
2. The ejector refrigeration according to claim 1, wherein in the other operation mode, the refrigerant is decompressed and expanded by the refrigerant depressurization means (18), and the refrigerant flow path is switched into a refrigerant flow path that flows into the one heat exchanger. cycle. The one compression mechanism is a first compression mechanism (11a),
The refrigerant flow switching means (31 to 33)
In the one operation mode, switching to the refrigerant flow path for evaporating the refrigerant flowing out of the diffuser part (14d) in the outflow side heat exchanger (52),
14. The refrigerant flow path for radiating the refrigerant discharged from the first compression mechanism (11a) in the outflow side heat exchanger (52) in the other operation mode is switched to the refrigerant flow path. Ejector refrigeration cycle. The one compression mechanism is a second compression mechanism (21a),
The refrigerant flow switching means (31 to 33)
In the one operation mode, switching to the refrigerant flow path for evaporating the refrigerant flowing out of the diffuser part (14d) in the outflow side heat exchanger (52),
The ejector-type refrigeration cycle according to claim 13, wherein, in the other operation mode, the refrigerant flow path is switched to a refrigerant flow path for evaporating the refrigerant flowing out from the one heat exchanger. First and second compression mechanisms (11a, 21a) for compressing and discharging the refrigerant;
A discharge side branching section (24) for branching the flow of the refrigerant discharged from the first compression mechanism (11a);
A heat dissipating heat exchanger (54) for dissipating one of the refrigerants branched at the discharge-side branch (24);
The refrigerant sucked from the refrigerant suction port (13b) by the flow of the high-speed jet refrigerant jetted from the nozzle portion (13a) for decompressing and expanding the refrigerant flowing out from the heat dissipation heat exchanger (54), An ejector (13) for increasing the pressure of the mixed refrigerant with the suction refrigerant sucked from the refrigerant suction port (13b) at the diffuser portion (13d);
An outdoor heat exchanger (41) for exchanging heat between the refrigerant and the outside air;
A use side heat exchanger (51) for exchanging heat between the refrigerant and the fluid to be heat exchanged;
Refrigerant decompression means (18) for decompressing and expanding the refrigerant;
A refrigerant channel switching means (31, 32) for switching a refrigerant channel in a cooling operation mode for cooling the fluid for heat exchange and a refrigerant channel in a heating operation mode for heating the fluid for heat exchange;
The refrigerant flow switching means (31, 32)
In one of the cooling operation mode and the heating operation mode, the other refrigerant branched in the discharge side branching section (24) is transferred to the outdoor heat exchanger (41) and the use side heat exchanger ( 51), heat is radiated by one of the heat exchangers, and the refrigerant radiated by the one of the heat exchangers is caused to flow into the refrigerant decompression means (18), and the outdoor heat exchanger (41) and the use side Of the heat exchanger (51), the refrigerant evaporated in the other heat exchanger is sucked into the second compression mechanism (21a) and switched to a refrigerant flow path for discharging to the refrigerant suction port (13b) side,
During the other operation mode of the cooling operation mode and the heating operation mode, the refrigerant discharged from one of the first and second compression mechanisms (11a, 21a) is transferred to the other heat exchanger. The refrigerant that has radiated heat at the other heat exchanger and that has radiated heat at the other heat exchanger flows into the refrigerant pressure reducing means (18), and at the same time the refrigerant that has evaporated at the one heat exchanger is sucked into the one compression mechanism An ejector type refrigeration cycle characterized by switching to a flow path.   An outflow side heat exchanger (52) that evaporates refrigerant that flows out of the diffuser section (13d) and is sucked into the first compression mechanism (11a) during the one operation mode. The ejector type refrigeration cycle according to 16. The one compression mechanism is a first compression mechanism (11a),
The refrigerant flow switching means (31, 32)
In the one operation mode, switching to the refrigerant flow path for evaporating the refrigerant flowing out of the diffuser part (14d) in the outflow side heat exchanger (52),
18. The ejector refrigeration according to claim 17, wherein, in the other operation mode, switching to a refrigerant flow path for evaporating refrigerant flowing out from the one heat exchanger in the outflow side heat exchanger (52). cycle. The one compression mechanism is a first compression mechanism (11a),
The refrigerant flow switching means (31, 32)
In the one operation mode, switching to the refrigerant flow path for evaporating the refrigerant flowing out of the diffuser part (14d) in the outflow side heat exchanger (52),
18. The ejector refrigeration according to claim 17, wherein, in the other operation mode, the refrigerant is switched to a refrigerant flow path that radiates the refrigerant discharged from the first compression mechanism (11 a) in the outflow side heat exchanger (52). cycle. The one compression mechanism is a second compression mechanism (21a),
The refrigerant flow switching means (31, 32)
In the one operation mode, switching to the refrigerant flow path for evaporating the refrigerant flowing out of the diffuser part (14d) in the outflow side heat exchanger (52),
18. The ejector refrigeration according to claim 17, wherein, in the other operation mode, switching to a refrigerant flow path for evaporating refrigerant flowing out from the one heat exchanger in the outflow side heat exchanger (52). cycle.   21. An internal heat exchanger for exchanging heat between the refrigerant flowing out of the one heat exchanger and the refrigerant sucked by the second compression mechanism (21a) during the one operation mode. The ejector-type refrigeration cycle according to any one of the above.   The ejector according to any one of claims 1 to 21, wherein the operation of the other compression mechanism of the first and second compression mechanisms (11a, 21a) is stopped during the other operation mode. Refrigeration cycle.   The ejector-type refrigeration cycle according to any one of claims 1 to 22, further comprising high-pressure side decompression means (19a) for decompressing and expanding the refrigerant flowing into the nozzle portion (13a). First discharge capacity changing means (11b) for changing the refrigerant discharge capacity of the first compression mechanism (11a);
Second discharge capacity changing means (21b) for changing the refrigerant discharge capacity of the second compression mechanism (21a);
The first discharge capacity changing means (11b) and the second discharge capacity changing means (21b) independently change the refrigerant discharge capacity of the first compression mechanism (11a) and the second compression mechanism (21a). The ejector-type refrigeration cycle according to any one of claims 1 to 23, wherein the ejector-type refrigeration cycle is configured to be possible.   The said 1st compression mechanism (11a) and the said 2nd compression mechanism (21a) are accommodated in the same housing, and are comprised integrally, The one of Claims 1 thru | or 24 characterized by the above-mentioned. The ejector-type refrigeration cycle described in 1.   The ejector-type refrigeration cycle according to any one of claims 1 to 25, wherein the first compression mechanism (11a) increases the pressure of the refrigerant until it reaches a critical pressure or more.

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