JP5195364B2 - Ejector refrigeration cycle - Google Patents

Description

  The present invention relates to an ejector-type refrigeration cycle in which the pressure of a refrigerant is increased in multiple stages and an ejector is provided as refrigerant decompression means.

  Conventionally, an economizer refrigeration cycle, an ejector refrigeration cycle, and the like proposed for improving the coefficient of performance (COP) of a vapor compression refrigeration cycle are known.

  For example, as an economizer-type refrigeration cycle, a high-stage decompression unit that decompresses and expands a high-pressure refrigerant, a gas-liquid separator that separates gas-liquid of an intermediate-pressure refrigerant decompressed by the high-stage decompression unit, and a gas-liquid separation A low-stage decompression unit that decompresses and expands the liquid-phase refrigerant separated in the vessel to form a low-pressure refrigerant, a low-stage compression unit that pressurizes the low-pressure refrigerant until it becomes an intermediate-pressure refrigerant, and an intermediate-pressure refrigerant as the high-pressure refrigerant. A cycle including a high-stage compression unit that boosts the pressure until it reaches is known.

  In this economizer-type refrigeration cycle, the refrigerant that has been pressurized by the low-stage compression means and the gas-phase refrigerant separated by the gas-liquid separator are mixed, and the mixed intermediate-pressure refrigerant is mixed with the high-pressure refrigerant by the latter-stage compression means. Thus, the pressure of the refrigerant is increased in multiple stages. As a result, the pressure difference between the suction pressure and the discharge pressure in each compression means is reduced compared with the case where the pressure of the low-pressure refrigerant is increased to a high-pressure refrigerant by a single compression means, and the compression efficiency of each compression means is reduced. Has improved.

  Further, for example, as an ejector-type refrigeration cycle, an ejector that decompresses and expands a high-pressure refrigerant, a gas-liquid separator that separates gas-liquid of the refrigerant decompressed by the ejector, and a liquid phase separated by the gas-liquid separator A cycle is known that includes decompression means that decompresses and expands the refrigerant and flows out to the evaporator inlet side, and compression means that pressurizes the gas-phase refrigerant separated by the gas-liquid separator until it becomes a high-pressure refrigerant.

  In this ejector-type refrigeration cycle, the refrigerant flowing out of the evaporator from the refrigerant suction port of the ejector is sucked by the pressure drop of the refrigerant injected from the nozzle part of the ejector, thereby reducing the kinetic energy loss during decompression expansion in the nozzle part. Collected. The recovered kinetic energy (hereinafter referred to as recovered energy) is converted into pressure energy by the diffuser portion of the ejector.

  As a result, for the refrigeration cycle that does not employ an ejector as the decompression means, the refrigerant pressure on the suction side of the compression means is increased above the refrigerant evaporation pressure in the evaporator, thereby reducing the driving power of the compression means.

Furthermore, Patent Document 1 discloses an ejector-type refrigeration cycle that employs an ejector as a means corresponding to the high-stage decompression means of the economizer-type refrigeration cycle. As a result, Patent Document 1 attempts to improve COP by simultaneously obtaining the effect of improving the compression efficiency in the above-described economizer refrigeration cycle and the effect of reducing the driving power of the compression means by the ejector.
Japanese Patent No. 4-320762

  By the way, as described above, the effect of improving the compression efficiency in the economizer refrigeration cycle is obtained by reducing the pressure difference between the suction pressure and the discharge pressure in each compression means. Therefore, in the economizer refrigeration cycle, in order to effectively improve COP, it is necessary to control the pressure of the intermediate pressure refrigerant to an appropriate value.

Here, in the ejector-type refrigeration cycle of Patent Document 1 shown in the overall configuration diagram of FIG. 32 , in order to control the pressure of the intermediate pressure refrigerant to an appropriate value, the suction side evaporator 19 and the refrigerant suction port 15 of the ejector 15 are used. It is necessary to appropriately adjust the opening degree of the flow rate adjusting means (flow rate adjusting valve) 38 disposed between “b” and “b”.

For example, in order to increase the pressure of the intermediate pressure refrigerant, the flow rate of the flow rate adjustment valve 38 is reduced, and the flow rate of the refrigerant sucked directly into the low-stage compression means 21a from the outlet side of the suction side evaporator 19 is increased. There must be. However, thus squeezing the opening of the flow regulating valve 38, the pressure loss of the refrigerant flow path from the suction side evaporator 19 to the refrigerant suction port 15 b of the ejector 15 is increased.

As a result, reduced suction flow rate of refrigerant sucked from the refrigerant suction port 15 b into the ejector 15 is recovered energy of the ejector 15 is also lowered. In other words, in the ejector refrigeration cycle of Patent Document 1, if the pressure of the intermediate pressure refrigerant is controlled to an appropriate value in order to obtain the effect of improving the compression efficiency in the economizer refrigeration cycle, the effect of reducing the driving power of the compression means by the ejector is sufficient. It becomes difficult to obtain.

  In other words, in the ejector type refrigeration cycle of Patent Document 1, it is difficult to control the operation of the cycle so as to simultaneously obtain the effect of improving the compression efficiency in the economizer type refrigeration cycle and the effect of reducing the driving power of the compression means by the ejector. There's a problem.

  In view of the above points, the present invention is to increase the refrigerant pressure in multiple stages and to sufficiently obtain both effects of improving the compression efficiency of the compression means and reducing the driving power in the ejector refrigeration cycle including the ejector. Objective.

In order to achieve the above object, in the first aspect of the present invention, the first compression means (11a) that compresses and discharges the refrigerant and the heat dissipation that dissipates the high-pressure refrigerant discharged from the first compression means (11a). Separator 12, high-stage decompression means 13 that decompresses and expands the high-pressure refrigerant that has flowed out of radiator 12, and gas-liquid refrigerant decompressed and expanded by high-stage decompression means 13 The intermediate pressure side gas-liquid separator (14) and the high-speed injected refrigerant flow injected from the nozzle portion (15a) for decompressing and expanding the liquid-phase refrigerant separated by the intermediate pressure side gas-liquid separator (14) Is sucked from the refrigerant suction port (15b), and the ejector (15) that mixes the injected refrigerant and the suction refrigerant sucked from the refrigerant suction port (15b) to increase the pressure, evaporates the refrigerant, 15b) Suction side evaporator (1 ) And second compression means (21a) for compressing and discharging the refrigerant flowing out of the ejector (15), the first compression means (11a) includes the refrigerant discharged from the second compression means (21a) and The intermediate pressure refrigerant mixed with the gas-phase refrigerant separated by the intermediate pressure side gas-liquid separator (14) is compressed and discharged , and the refrigerant discharge capacity of the first compression means (11a) is changed. The first discharge capacity changing means (11b), the second discharge capacity changing means (21b) for changing the refrigerant discharge capacity of the second compression means (21a), the first discharge capacity changing means (11b) and the second discharge. Control means for controlling the capacity changing means (21b), the first discharge capacity changing means (11b) and the second discharge capacity changing means (21b) being independently the first compression means (11a) and the second Compression means (21a) The refrigerant discharge capacity is configured to be changeable, and the control means changes the first discharge capacity so that the pressure increase amount in the first compression mechanism (11a) is equal to the pressure increase amount in the second compression mechanism (21a). It is characterized by an ejector refrigeration cycle for controlling the means (11b) and the second discharge capacity changing means (21b) .

According to this, the suction pressure and the discharge pressure in the first and second compression means (11a, 21a) can be easily changed by appropriately changing the refrigerant discharge capacity of the first and second compression means (11a, 21a). By controlling the intermediate pressure so as to reduce the pressure difference between the two, a compression efficiency improvement effect similar to that of the economizer refrigeration cycle can be obtained.
In particular, in the first aspect of the invention, the first discharge capacity changing means is controlled by the control means so that the pressure increase amount in the first compression mechanism (11a) is equal to the pressure increase amount in the second compression mechanism (21a). (11b) and the second discharge capacity changing means (21b) are controlled to improve both the compression efficiency of the first and second compression mechanisms (11a, 21a), and to reduce the COP as the whole ejector refrigeration cycle. It can be close to the maximum.

  Moreover, even if the refrigerant discharge capacities of the first and second compression means (11a, 21a) are changed, the pressure loss in the refrigerant passage from the suction side evaporator (19) to the refrigerant suction port (15b) of the ejector (15). Does not change. Therefore, even if the refrigerant discharge capacities of the first and second compression means (11a, 21a) are changed, the driving power reduction effect of the compression means by the ejector (15) can be obtained.

As a result, both the compression efficiency improvement effect and the driving power reduction effect of the compression means can be sufficiently obtained, and the COP of the ejector refrigeration cycle can be effectively improved.
Furthermore, since the saturated gas phase refrigerant can be sucked into the first compression means (11a) from the gas phase refrigerant outlet of the intermediate pressure side gas-liquid separator (14), only the refrigerant discharged from the second compression means (21a) is sucked. In contrast, the COP can be further improved by reducing the compression work when the refrigerant is isentropically compressed in the first compression means (11a).

  According to a second aspect of the present invention, in the ejector-type refrigeration cycle according to the first aspect, an outflow-side gas-liquid separator (17) that separates the gas-liquid refrigerant flowing out of the ejector (15), and the outflow-side gas-liquid The liquid phase refrigerant separated by the separator (17) is decompressed and expanded, and is provided with suction side pressure reducing means (18) for flowing out to the inlet side of the suction side evaporator (19).

  Specifically, the refrigerant is supplied from the outflow side gas-liquid separator (17) to the suction side evaporator (19) via the suction side pressure reducing means (18), and the suction side evaporator (19). Can demonstrate the refrigerating capacity.

  According to a third aspect of the present invention, in the ejector-type refrigeration cycle according to the second aspect, the ejector-type refrigeration cycle is disposed between the outlet side of the ejector (15) and the suction side of the second compression means (21a), and from the ejector (15). An outflow side evaporator (16) for evaporating the outflowed refrigerant is provided. According to this, not only the suction side evaporator (19) but also the outflow side evaporator (16) can exhibit the refrigerating capacity.

  Further, in the suction side evaporator (19), the refrigerant evaporating pressure corresponds to the suction action of the injected refrigerant, and in the outflow side evaporator (16), the refrigerant evaporating pressure after being boosted by the boosting action of the ejector (15) Therefore, the refrigerant evaporation temperatures of the outflow side evaporator (16) and the suction side evaporator (19) can be set to different temperatures.

  According to a fourth aspect of the present invention, in the ejector refrigeration cycle according to the first aspect, the branch part (32) for branching the flow of the refrigerant flowing out from the ejector (15), and one outlet of the branch part (32) An outlet side evaporator (16) disposed between the suction side and the suction side of the second compression means (21a) and evaporating one refrigerant branched at the branch portion (32); and a branch portion (32) And suction side decompression means (18) for decompressing and expanding the other branched refrigerant to flow out to the suction side evaporator (19) inlet side.

  According to this, specifically, the refrigerant is supplied to both the outflow side evaporator (16) and the suction side evaporator (19), and the refrigerating capacity is exhibited in both the evaporators (16, 19). Can do. Further, similarly to the third aspect of the invention, the refrigerant evaporation temperatures of both evaporators (16, 19) can be set to different temperatures.

  According to a fifth aspect of the present invention, in the ejector refrigeration cycle according to any one of the first to fourth aspects, the liquid phase refrigerant separated by the intermediate pressure side gas-liquid separator (14) and the low pressure side of the cycle An internal heat exchanger (30) for exchanging heat with the refrigerant is provided. According to this, the enthalpy difference (refrigeration capacity) between the enthalpy of the inlet side refrigerant (19) inlet side refrigerant and the enthalpy of outlet side refrigerant can be expanded, and COP can be improved.

  Specifically, the low-pressure side refrigerant of the cycle may be a refrigerant sucked into the refrigerant suction port (15b) as in the invention described in claim 6, or as in the invention described in claim 7. The refrigerant may be sucked into the second compression means (21a).

  In the invention according to claim 8, in the ejector refrigeration cycle according to claim 1, a branch portion (22) for branching the flow of the liquid-phase refrigerant separated by the intermediate pressure side gas-liquid separator (14), A suction side decompression means (18) for decompressing and expanding the refrigerant flowing into the suction side evaporator (19), and the nozzle portion (15a) decompresses and expands one of the refrigerants branched at the branch portion (22). The suction-side decompression means (18) is characterized by decompressing and expanding the other refrigerant branched at the branch portion (22).

  According to this, specifically, the refrigerant is supplied from the intermediate pressure side gas-liquid separator (14) to the suction side evaporator (19) via the branching portion (22) and the suction side pressure reducing means (18) for suction. The refrigerating capacity can be exhibited in the side evaporator (19).

  According to the ninth aspect of the present invention, in the ejector refrigeration cycle according to the eighth aspect, the ejector is disposed between the outlet side of the ejector (15) and the suction side of the second compression means (21a), and from the ejector (15). An outflow side evaporator (16) for evaporating the outflowed refrigerant is provided.

  According to this, not only the suction side evaporator (19) but also the outflow side evaporator (16) can exhibit the refrigerating capacity. Furthermore, similarly to the third aspect of the invention, the refrigerant evaporation temperatures of the outflow side evaporator (16) and the suction side evaporator (19) can be set to different temperatures.

  According to a tenth aspect of the present invention, in the ejector refrigeration cycle according to the eighth or ninth aspect, the other liquid-phase refrigerant branched at the branching section (22) and the low-pressure side refrigerant of the cycle exchange heat. It is provided with a heat exchanger (30). According to this, the enthalpy difference (refrigeration capacity) between the enthalpy of the inlet side refrigerant (19) inlet side refrigerant and the enthalpy of outlet side refrigerant can be expanded, and COP can be improved.

  According to an eleventh aspect of the invention, in the ejector refrigeration cycle according to the eighth or ninth aspect, internal heat exchange is performed in which heat is exchanged between the refrigerant in the decompression expansion process in the suction side decompression means (18) and the low-pressure side refrigerant in the cycle. It is provided with a vessel (31). According to this, the enthalpy difference (refrigeration capacity) between the enthalpy of the inlet side refrigerant (19) inlet side refrigerant and the enthalpy of outlet side refrigerant can be expanded, and COP can be improved.

  Specifically, the low-pressure side refrigerant of the cycle may be a refrigerant sucked into the refrigerant suction port (15b) as in the invention described in claim 12, or as in the invention described in claim 13. The refrigerant may be sucked into the second compression means (21a).

  In the invention described in claim 14, in the ejector-type refrigeration cycle described in claim 1, the first branch configured to be able to branch the flow of the liquid phase refrigerant separated by the intermediate pressure side gas-liquid separator (14). Part (22), a second branch part (32) configured to be able to branch the flow of the refrigerant flowing out from the ejector (15), one outlet side of the second branch part (32), and a second compression means ( 21a) An outlet-side evaporator (16) disposed between the suction side and evaporating one of the refrigerants branched at the second branch portion (32), and a refrigerant flowing into the suction-side evaporator (19) First and second suction side decompression means (18, 28) for decompressing and expanding, and the nozzle section (15a) decompresses and expands one of the refrigerants branched at the first branch section (22), The one suction side pressure reducing means (18) is the other branched at the first branch (22). The medium is decompressed and expanded, the second suction-side decompression means (28) decompresses and expands the other refrigerant branched by the second branching section (32), and the suction-side evaporator (19) It is characterized in that at least one of the refrigerant decompressed and expanded by the two suction side decompression means (18, 28) is evaporated.

  According to this, the refrigerant flow is branched only by the first branch portion (22), the refrigerant flowing out from the first suction side pressure reducing means (18) is supplied to the suction side evaporator (19), and the ejector ( 15) By supplying the refrigerant that has flowed out from the outlet side to the outlet side evaporator (16) through the second branch portion (32), both the outlet side evaporator (16) and the suction side evaporator (19) A cycle configuration that demonstrates the refrigerating capacity can be realized.

  Further, the refrigerant flow is branched only by the second branch section (32), and the refrigerant flowing out from the ejector (15) is supplied to both the outflow side evaporator (16) and the suction side evaporator (19). Thus, it is possible to realize a cycle configuration in which both the outflow side evaporator (16) and the suction side evaporator (19) exhibit refrigeration capacity.

  Furthermore, by branching the flow of the refrigerant in both the first and second branch parts (22, 32) and supplying the refrigerant to both the outflow side evaporator (16) and the suction side evaporator (19), A cycle configuration in which the refrigerating capacity is exhibited in both the outflow side evaporator (16) and the suction side evaporator (19) can be realized. In each cycle configuration, the refrigerant evaporating temperatures of the outflow side evaporator (16) and the suction side evaporator (19) can be set to different temperatures, as in the third aspect of the invention.

  According to a fifteenth aspect of the present invention, in the ejector refrigeration cycle according to the fourteenth aspect, the other liquid-phase refrigerant branched at the first branch portion (22) and the low-pressure side refrigerant of the cycle exchange heat. It is provided with a heat exchanger (30).

  According to this, the enthalpy difference (refrigeration capacity) between the enthalpy of the inlet side refrigerant and the enthalpy of the outlet side refrigerant of both the evaporators (16, 19) of the outflow side evaporator (16) and the suction side evaporator (19) is obtained. It can be expanded to improve COP.

  Specifically, the low-pressure side refrigerant of the cycle may be a refrigerant sucked into the refrigerant suction port (15b) as in the invention described in claim 16, or as in the invention described in claim 17. The refrigerant may be sucked into the second compression means (21a).

In the invention according to claim 18, the first compression means (11a) for compressing and discharging the refrigerant, the radiator (12) for dissipating the high-pressure refrigerant discharged from the first compression means (11a), High-speed injection that injects from the branch part (22) that branches the flow of the refrigerant that has flowed out of the radiator (12) and the nozzle part (15a) that decompresses and expands one of the refrigerants branched by the branch part (22) An ejector (15) that sucks the refrigerant from the refrigerant suction port (15b) by the flow of the refrigerant, mixes the injected refrigerant and the suction refrigerant sucked from the refrigerant suction port (15b), and boosts the pressure; and a branch portion (22) An auxiliary radiator (12e) for radiating the other refrigerant branched at, a high stage pressure reducing means (13) for decompressing and expanding the refrigerant flowing out from the auxiliary radiator (12e), and a high stage pressure reducing means (13 ) Of the refrigerant expanded under reduced pressure An intermediate pressure side gas-liquid separator (14) for separating liquid, a suction side pressure reducing means (18) for decompressing and expanding the liquid-phase refrigerant separated by the intermediate pressure side gas-liquid separator (14), and a suction side pressure reducing means ( 18) evaporating the refrigerant decompressed and expanded in step 18), evaporating the refrigerant to the refrigerant suction port (15b) side, and second compression for compressing and discharging the refrigerant flowing out from the ejector (15) Means (21a), wherein the first compression means (11a) mixed the refrigerant discharged from the second compression means (21a) and the gas-phase refrigerant separated by the intermediate pressure side gas-liquid separator (14). The intermediate pressure refrigerant is compressed and discharged , and the first discharge capacity changing means (11b) for changing the refrigerant discharge capacity of the first compression means (11a) and the second compression means (21a) Second discharge capacity changing means for changing the refrigerant discharge capacity ( 1b) and control means for controlling the first discharge capacity changing means (11b) and the second discharge capacity changing means (21b), the first discharge capacity changing means (11b) and the second discharge capacity changing means (21b). ) Are configured such that the refrigerant discharge capacities of the first compression means (11a) and the second compression means (21a) can be changed independently of each other, and the control means can increase the amount of pressure increase in the first compression mechanism (11a). And an ejector-type refrigeration cycle that controls the first discharge capacity changing means (11b) and the second discharge capacity changing means (21b) so that the pressure increase amounts in the second compression mechanism (21a) are equal .

  According to this, similarly to the first aspect of the invention, it is possible to obtain the same compression efficiency improvement effect as that of the economizer refrigeration cycle by appropriately controlling the intermediate pressure, and by the boosting action of the ejector (15). The driving power reduction effect of the compression means can be obtained at the same time. As a result, it is possible to sufficiently obtain both the effect of improving the compression efficiency of the compression means and the effect of reducing the driving power.

  More specifically, the suction side evaporator is configured by supplying the refrigerant from the intermediate pressure side gas-liquid separator (14) to the suction side evaporator (19) via the branching portion (22) and the suction side pressure reducing means (18). The refrigerating capacity can be exhibited in (19).

  At this time, since the low enthalpy refrigerant cooled by both the radiator (12) and the auxiliary radiator (12e) can flow into the suction side evaporator (19), the suction side evaporator (19) inlet side COP can be improved by expanding the enthalpy difference (refrigeration capacity) between the enthalpy of the refrigerant and the enthalpy of the outlet side refrigerant.

  Moreover, since the refrigerant flowing into the nozzle part (15a) of the ejector (15) is not cooled by the auxiliary radiator (12e), the enthalpy does not decrease with respect to the refrigerant flowing into the suction side pressure reducing means (18). Thereby, the amount of recovered energy in the nozzle part (15a) can be increased, and the COP can be further improved.

According to the nineteenth aspect of the present invention, the first compression means (11a) that compresses and discharges the refrigerant, and the branch portion (22) that branches the flow of the high-pressure refrigerant discharged from the first compression means (11a). And the first radiator (121) that radiates one of the refrigerants branched at the branching part (22), and the refrigerant that flows out from the first radiator (121) is injected from the nozzle part (15a) that decompresses and expands. An ejector (15) for sucking the refrigerant from the refrigerant suction port (15b) by the flow of the high-speed jet refrigerant, mixing the jetted refrigerant and the suction refrigerant sucked from the refrigerant suction port (15b), and increasing the pressure; A second radiator (122) that radiates the other refrigerant branched at the section (22), a high-stage decompression means (13) that decompresses and expands the high-pressure refrigerant that has flowed out of the second radiator (122), Depressurization with high-stage depressurization means (13) An intermediate-pressure side gas-liquid separator (14) for separating the gas-liquid of the stretched refrigerant, and a suction-side pressure-reducing means (18) for decompressing and expanding the liquid-phase refrigerant separated by the intermediate-pressure side gas-liquid separator (14) The refrigerant flowing out from the suction side pressure reducing means (18) is evaporated and the refrigerant flowing out from the suction side evaporator (19) and the ejector (15) are compressed and discharged. A second compression means (21a), wherein the first compression means (11a) is a gas phase refrigerant separated from the refrigerant discharged from the second compression means (21a) and the intermediate pressure side gas-liquid separator (14). The intermediate pressure refrigerant mixed with the first compression means (11a) is compressed and discharged, and the first discharge capacity changing means (11b) for changing the refrigerant discharge capacity of the first compression means (11a) and the second compression means ( 21a) The second discharge capacity for changing the refrigerant discharge capacity And a control means for controlling the first discharge capacity changing means (11b) and the second discharge capacity changing means (21b), the first discharge capacity changing means (11b) and the second discharge capacity changing. The means (21b) is configured such that the refrigerant discharge capacities of the first compression means (11a) and the second compression means (21a) can be changed independently, and the control means is the first compression mechanism (11a). It features an ejector type refrigeration cycle that controls the first discharge capacity changing means (11b) and the second discharge capacity changing means (21b) so that the pressure increase quantity at the second compression mechanism (21a) is equal to To do.

  According to this, similarly to the first aspect of the invention, it is possible to obtain the same compression efficiency improvement effect as that of the economizer refrigeration cycle by appropriately controlling the intermediate pressure, and by the boosting action of the ejector (15). The driving power reduction effect of the compression means can be obtained at the same time. As a result, it is possible to sufficiently obtain both the effect of improving the compression efficiency of the compression means and the effect of reducing the driving power.

  More specifically, the suction side evaporator is configured by supplying the refrigerant from the intermediate pressure side gas-liquid separator (14) to the suction side evaporator (19) via the branching portion (22) and the suction side pressure reducing means (18). The refrigerating capacity can be exhibited in (19).

  At this time, since the heat exchange capability (heat dissipation capability) of the first radiator (121) and the second radiator (122) can be changed independently, the heat exchange capability of the second radiator (122) and the suction The heat exchange capacity (endothermic performance) of the side evaporator (19) can be easily adapted. Therefore, it is easy to stabilize the operation of the cycle.

  Moreover, the enthalpy of the refrigerant | coolant which flows in into the nozzle part (15a) of an ejector (15) is employ | adopted as the 1st radiator (121) by the thing whose heat exchange capability is lower than a 2nd radiator (122). Unnecessary decrease can be avoided. Thereby, the amount of recovered energy in the nozzle part (15a) can be increased, and COP can be improved.

  According to a twentieth aspect of the present invention, in the ejector refrigeration cycle according to the eighteenth or nineteenth aspect, the ejector (15) is disposed between the outlet side of the ejector (15) and the suction side of the second compression means (21a). It has an outflow side evaporator (16) for evaporating the refrigerant that has flowed out of the apparatus.

  According to this, not only the suction side evaporator (19) but also the outflow side evaporator (16) can exhibit the refrigerating capacity. Furthermore, similarly to the third aspect of the invention, the refrigerant evaporation temperatures of the outflow side evaporator (16) and the suction side evaporator (19) can be set to different temperatures.

  In the invention according to claim 21, in the ejector refrigeration cycle according to any one of claims 18 to 20, the liquid-phase refrigerant flowing out from the intermediate pressure-side gas-liquid separator (14), the low-pressure side refrigerant of the cycle, An internal heat exchanger (30) for exchanging heat is provided. According to this, the enthalpy difference (refrigeration capacity) between the enthalpy of the inlet side refrigerant (19) inlet side refrigerant and the enthalpy of outlet side refrigerant can be expanded, and COP can be improved.

  Specifically, the low-pressure side refrigerant of the cycle may be a refrigerant sucked into the refrigerant suction port (15b) as in the invention described in claim 22, or as in the invention described in claim 23. The refrigerant may be sucked into the second compression means (21a).

  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, the high-pressure side refrigerant discharged from the first compression means (11a) is supplied to the suction-side evaporator. A bypass passage (25) leading to (19) and an opening / closing means (26) for opening and closing the bypass passage (25) are provided.

  According to this, when the suction side evaporator (16) is frosted, the high temperature refrigerant discharged from the first compression means (11a) flows into the suction side evaporator (16) by opening the opening / closing means (26). Can be defrosted.

In the invention according to claim 25, the first compression means (11a) for compressing and discharging the refrigerant, the use-side heat exchanger (54) for exchanging heat between the refrigerant and the heat exchange target fluid, the refrigerant, Refrigerant channel switching for switching between an outdoor heat exchanger (53) for exchanging heat with the outside air, a refrigerant channel in a cooling operation mode for cooling the fluid to be heat exchanged, and a refrigerant channel in a heating operation mode for heating the fluid to be heat exchanged The high pressure that decompresses and expands the refrigerant radiated in the outdoor heat exchanger (53) or the use side heat exchanger (54) during at least one of the means (51, 52) and the cooling operation mode and the heating operation mode. A side pressure reducing means (13), an intermediate pressure side gas / liquid separator (14) for separating the gas / liquid of the refrigerant decompressed and expanded by the high pressure side pressure reducing means (13), and an intermediate pressure side gas / liquid separator (14). Reduce the pressure of the separated liquid refrigerant The refrigerant is sucked from the refrigerant suction port (15b) by the flow of the high-speed jet refrigerant jetted from the nozzle portion (15a) to be stretched, and the jetted refrigerant and the suction refrigerant sucked from the refrigerant suction port (15b) are mixed. And a second compression means (21a) for compressing and discharging the refrigerant flowing out of the ejector (15),
The first compression means (11a) compresses and discharges the intermediate pressure refrigerant obtained by mixing the refrigerant discharged from the second compression means (21a) and the gas-phase refrigerant separated by the intermediate pressure side gas-liquid separator (14). And
In the cooling operation mode, the refrigerant flow switching means (51, 52) radiates the refrigerant discharged from the first compression means (11a) in the outdoor heat exchanger (53) and uses the heat exchanger (54). ) Is switched to a refrigerant flow path that guides the refrigerant flowing out from the refrigerant suction port (15b), and in the heating operation mode, the refrigerant discharged from the first compression means (11a) is radiated by the use side heat exchanger (54). In addition, the refrigerant flowing out of the outdoor heat exchanger (53) is switched to the refrigerant flow path that guides the refrigerant to the refrigerant suction port (15b) side, and the refrigerant discharge capacity of the first compression means (11a) is changed. The first discharge capacity changing means (11b), the second discharge capacity changing means (21b) for changing the refrigerant discharge capacity of the second compression means (21a), the first discharge capacity changing means (11b) and the second discharge. Ability change means ( 1b), and the first discharge capacity changing means (11b) and the second discharge capacity changing means (21b) are respectively independently the first compression means (11a) and the second compression means (21a). ) Is configured to be able to change the refrigerant discharge capacity, and the control means performs the first discharge so that the pressure increase amount in the first compression mechanism (11a) is equal to the pressure increase amount in the second compression mechanism (21a). It is characterized by an ejector refrigeration cycle that controls the capacity changing means (11b) and the second discharge capacity changing means (21b) .

According to this, in both the cooling operation mode and the heating operation mode, by appropriately changing the refrigerant discharge capacity of the first and second compression means (11a, 21a), the first, By controlling the intermediate pressure so as to reduce the pressure difference between the suction pressure and the discharge pressure in the second compression means (11a, 21a), it is possible to obtain the same compression efficiency improvement effect as in the economizer refrigeration cycle.
Also in the invention of claim 25, as in the case of claim 1, the control means makes the pressure increase amount in the first compression mechanism (11a) and the pressure increase amount in the second compression mechanism (21a) equal by the control means. By controlling the first discharge capacity changing means (11b) and the second discharge capacity changing means (21b), both the compression efficiency of the first and second compression mechanisms (11a, 21a) are improved, and the ejector refrigeration cycle. The COP as a whole can be brought close to the maximum.

  Moreover, at this time, even if the refrigerant discharge capacities of the first and second compression means (11a, 21a) are changed, the refrigerant passage from the suction side evaporator (19) to the refrigerant suction port (15b) of the ejector (15). The pressure loss is not changed. Therefore, even if the refrigerant discharge capacities of the first and second compression means (11a, 21a) are changed, the driving power reduction effect of the compression means by the ejector (15) can be obtained.

  As a result, both the compression efficiency improvement effect and the driving power reduction effect of the compression means can be sufficiently obtained, and the COP of the ejector refrigeration cycle can be effectively improved.

Further, specifically, as in the invention described in claim 26, in the ejector-type refrigeration cycle according to claim 25, an outflow-side gas-liquid separator that separates the gas-liquid refrigerant flowing out of the ejector (15) ( 17), the gas phase refrigerant outlet of the outflow side gas-liquid separator (17) is connected to the suction port side of the second compression means (21a),
In the cooling operation mode, the refrigerant flow switching means (51, 52) causes the refrigerant radiated by the outdoor heat exchanger (53) to flow into the high-pressure side pressure reducing means (13) and the outflow-side gas-liquid separator (17). ) Is switched to a refrigerant flow path through which the liquid phase refrigerant separated in step) flows into the use side heat exchanger (54). In the heating operation mode, the refrigerant radiated by the use side heat exchanger (54) 13), and the liquid phase refrigerant separated by the outflow side gas-liquid separator (17) may be switched to a refrigerant flow path for flowing into the outdoor heat exchanger (53).

In the invention according to claim 2 7, in the ejector type refrigeration cycle according to any one of claims 1 to 26, the first compression means (11a) and the second compression means (21a) is in the same housing And is configured integrally. According to this, the first compression means (11a) and the second compression means (21a) can be reduced in size, and the entire ejector refrigeration cycle can be reduced in size.

As in the invention described in claim 28 , in the ejector refrigeration cycle according to any one of claims 1 to 27 , the first compression means (11a) increases the pressure of the refrigerant until it reaches a critical pressure or higher. 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.

(First embodiment)
An example in which the ejector refrigeration cycle of the present invention is applied to a refrigerator will be described with reference to FIGS. This refrigerator cools the inside of a freezer that is a space to be cooled to an extremely low temperature of about −30 to −10 ° C. FIG. 1 is an overall configuration diagram of an ejector refrigeration cycle 100 of the present embodiment.

  In the ejector-type refrigeration cycle 100, the compressor 10 sucks refrigerant and boosts and discharges the refrigerant in multiple stages. Specifically, the compressor 10 of the present embodiment drives the first and second compression units 11a and 21a and the first and second compression units 11a and 21a in a single housing 10a. 1 is a two-stage booster type electric compressor configured to accommodate the second electric motors 11b and 21b.

  As the first and second compression means 11a and 21a, various compression mechanisms such as scroll-type compression means and vane-type compression means can be employed. The first and second electric motors 11b and 21b are each independently controlled in operation (number of rotations) by a control signal output from a control device to be described later. Any format may be adopted.

  And by this rotation speed control, the refrigerant | coolant discharge capability of the 1st, 2nd compression means 11a and 21a is each changed independently. Accordingly, the first and second electric motors 11b and 21b of the present embodiment constitute first and second discharge capacity changing means for changing the refrigerant discharge capacity of the first and second compression means 11a and 21a, respectively. .

  The housing 10a is provided with a suction port 10b for sucking low-pressure refrigerant, an intermediate-pressure port 10c for flowing intermediate-pressure refrigerant, and a discharge port 10d for discharging high-pressure refrigerant. These ports 10b to 10d are connected to the first and second compression means 11a and 21a inside the housing 10a.

  Specifically, the suction port 10b is connected to the suction port of the second compression means 21a, and the intermediate pressure port 10c is communicated with the discharge port of the second compression means 21a and the suction port of the first compression means 11a. The discharge port 10d is connected to the discharge port of the first compression means 11a. Therefore, the first compression unit 11a sucks, compresses and discharges the intermediate pressure refrigerant obtained by mixing the refrigerant discharged from the second compression unit 21a and the refrigerant flowing in from the intermediate pressure port 10c.

  Further, as shown in FIG. 1, a radiator 12 is connected to the discharge port 10 d of the compressor 10. The radiator 12 is a heat exchanger for heat radiation that radiates and cools the high-pressure refrigerant by exchanging heat between the high-pressure refrigerant discharged from the compressor 10 and outside air (outside air) blown by the cooling fan 12a. . The cooling fan 12a is an electric blower in which the number of rotations (the amount of blown air) is controlled by a control voltage output from the control device.

  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. Therefore, the radiator 12 functions as a condenser that condenses the refrigerant.

  A fixed throttle 13 as a high pressure side pressure reducing means is connected to the outlet side of the radiator 12. As the fixed throttle 13, a capillary tube, an orifice, or the like can be used. An intermediate pressure side gas-liquid separator 14 is connected to the outlet side of the fixed throttle 13. The intermediate pressure side gas-liquid separator 14 separates the gas-liquid refrigerant flowing out from the fixed throttle 13 and stores excess liquid-phase refrigerant.

  An intermediate pressure port 10 c of the compressor 10 is connected to the gas phase refrigerant outlet of the intermediate pressure side gas-liquid separator 14. Furthermore, an ejector 15 is connected to the liquid-phase refrigerant outlet of the intermediate pressure side gas-liquid separator 14. The ejector 15 is a refrigerant decompression unit that decompresses and expands the refrigerant, and is also a refrigerant circulation unit that circulates the refrigerant by a suction action of a refrigerant flow ejected at a high speed.

  Specifically, the ejector 15 reduces the passage area of the liquid-phase refrigerant flowing out from the intermediate pressure side gas-liquid separator 14 to reduce the passage area of the liquid-phase refrigerant in an isentropic manner. The refrigerant suction port 15b is disposed so as to communicate with the refrigerant injection port and sucks the refrigerant flowing out from a suction side evaporator 19 described later.

  Further, a diffuser portion 15c that mixes the high-speed refrigerant flow ejected from the nozzle portion 15a and the suction refrigerant from the refrigerant suction port 15b to increase the pressure at the downstream portion of the nozzle portion 15a and the refrigerant suction port 15b. Is provided.

  The diffuser portion 15c is formed in a shape that gradually increases the refrigerant passage area, and acts to decelerate the refrigerant flow to increase the refrigerant pressure, that is, to convert the velocity energy of the refrigerant into pressure energy. Further, an accumulator 17 is connected to the outlet side of the diffuser portion 15c.

  The accumulator 17 is an outflow-side gas-liquid separator that separates the gas-liquid refrigerant flowing out of the diffuser portion 15c and stores excess liquid-phase refrigerant in the cycle. A suction port 10 b of the compressor 10 is connected to the gas-phase refrigerant outlet of the accumulator 17, and a suction side evaporator 19 is connected to the liquid-phase refrigerant outlet via an electric variable throttle mechanism 18. Yes.

  The variable throttle mechanism 18 is a suction-side decompression unit that further decompresses and expands the liquid refrigerant flowing out of the accumulator 17. More specifically, the variable throttle mechanism 18 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. Yes. The operation of the variable aperture mechanism 18 is controlled by a control signal output from the control device.

  The suction-side evaporator 19 evaporates the low-pressure refrigerant and exhibits a heat-absorbing effect by exchanging heat between the low-pressure refrigerant decompressed and expanded by the variable throttle mechanism 18 and the freezer air circulated by the blower fan 19a. This is an endothermic heat exchanger. Therefore, in this embodiment, the air in a freezer becomes a heat exchange target fluid.

  The blower fan 19a 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. A refrigerant suction port 15 b of the ejector 15 is connected to the outlet side of the suction side evaporator 19.

  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 operations of the various electric actuators 11b, 12a, 18, 19a, 21b and the like described above.

  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. It also has a function as a second discharge capacity control means for controlling the above. Of course, the first discharge capacity control means and the second discharge capacity control means may be configured by different control devices.

  In addition, the control device is provided with a detection value of a sensor group (not shown) such as an outside air sensor for detecting the outside air temperature, an inside temperature sensor for detecting the inside temperature, an operation switch for operating the refrigerator, and the like. Various operation signals from an operation panel (not shown) are input.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. When the operation switch of the operation panel is turned on, the control device operates the first and second electric motors 11b and 21b, the cooling fan 12a, the variable throttle mechanism 18, and the blower fan 19a. Thereby, the compressor 10 sucks the refrigerant, compresses it, and discharges it.

At this time, the first refrigerant discharged from the compression means 11a state of the compressor 10 is a _2-point in FIG. The high-temperature and high-pressure gas-phase refrigerant discharged from the first compression means 11a flows into the radiator 12, exchanges heat with the blown air (outside air) blown from the cooling fan 12a, dissipates heat and condenses (a ₂ points → b ₂ points). The refrigerant radiated by the radiator 12 flows into the fixed throttle 13 and is decompressed and expanded in an enthalpy manner until reaching an intermediate pressure (b ₂ point → c ₂ point).

The intermediate pressure refrigerant flowing out of the fixed throttle 13 flows into the intermediate pressure side gas-liquid separator 14 and is separated into a gas phase refrigerant and a liquid phase refrigerant (points c ₂ → d ₂ and c ₂ → e ₂ ). . The gas phase refrigerant flowing out from the gas phase refrigerant outlet of the intermediate pressure side gas-liquid separator 14 flows into the compressor 10 through the intermediate pressure port 10 c of the compressor 10.

Further, the liquid phase refrigerant flowing out from the liquid phase refrigerant outlet of the intermediate pressure side gas-liquid separator 14 flows into the nozzle portion 15a of the ejector 15 and isentropically decompressed and expanded (point e ₂ → f ₂ ). 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 15a. Due to the refrigerant suction action of the injected refrigerant, the refrigerant that has flowed out of the suction side evaporator 19 from the refrigerant suction port 15b is sucked.

Then, the refrigerant injected from the nozzle portion 15a and the suction refrigerant sucked from the refrigerant suction port 15b flow into the diffuser portion 15c of the ejector 15 and are mixed (f ₂ point → g ₂ point and l ₂ point → g ₂ points). In the diffuser portion 15c, the refrigerant pressure energy rises (g ₂ point → h ₂ point) because the velocity energy of the refrigerant is converted into pressure energy due to the expansion of the passage area.

Next, the refrigerant that has flowed out of the diffuser portion 15c flows into the accumulator 17 and is separated into a gas-phase refrigerant and a liquid-phase refrigerant (h ₂ point → i ₂ point and h ₂ point → j ₂ point). The liquid-phase refrigerant that has flowed out of the liquid-phase refrigerant outlet of the accumulator 17 is further decompressed and expanded isothermally by the variable throttle mechanism 18 to reduce its pressure (j ₂ point → k ₂ point).

Variable decompressed and expanded refrigerant is in throttle mechanism 18, and flows into the suction side evaporator 19, the air blowing fan 19a is evaporated by absorbing heat from the internal air circulated blown (k ₂ points → l ₂ points). Thereby, the air in a warehouse is cooled. At this time, the control device adjusts the throttle opening degree of the variable throttle mechanism 18 so that the refrigerant evaporation temperature in the suction side evaporator 19 becomes the temperature set on the operation panel.

On the other hand, the gas-phase refrigerant that has flowed out from the gas-phase refrigerant outlet of the accumulator 17 is sucked into the second compression means 21a of the compressor 10, and is compressed and increased in pressure until it reaches an intermediate pressure (i ₂ point → m ₂ point). . The intermediate pressure refrigerant whose pressure has been increased by the second compression means 21a is mixed with the refrigerant flowing out from the gas phase refrigerant outlet of the intermediate pressure side gas-liquid separator 14 in the compressor 10 (m ₂ point → n ₂ point and d). ₂ points → n ₂ points). The mixed refrigerant is sucked into the first compression means 11a and compressed again (n ₂ point → a 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 100 as a whole approaches the maximum. Specifically, in order to improve the mechanical efficiency of the first and second compression units 11a and 21a, that is, the compression efficiency , the boosting amounts of the first and second compression units 11a and 21a are controlled to be substantially equal. To do.

  Note that the compression efficiency means that the amount of increase ΔH1 is actually calculated when ΔH1 is the amount of increase in the enthalpy of the refrigerant when the refrigerant is isentropically compressed by the first and second compression means 11a, 21a. 1, the value divided by the enthalpy increase ΔH2 of the refrigerant when the refrigerant is pressurized by the second compression means 11a, 21a.

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

  Since the ejector-type refrigeration cycle 100 of this embodiment operates as described above, the suction side evaporator 19 can cause the refrigerant to exhibit an endothermic effect to cool the inside of the freezer.

  Furthermore, since the refrigerant discharge capacities of the first and second compression means 11a and 21a are independently controlled, the pressure difference between the suction pressure and the discharge pressure in the first and second compression means 11a and 21a is very easily achieved. By controlling the intermediate pressure so as to reduce the pressure, it is possible to obtain the same compression efficiency improvement effect as in the above-described economizer refrigeration cycle.

  At this time, even if the refrigerant discharge capacities of the first and second compression means 11a and 21a are changed, the pressure loss in the refrigerant passage from the suction side evaporator 19 to the refrigerant suction port 15b of the ejector 15 does not change. Even if the refrigerant discharge capacity of the second compression means 11a, 21a is changed, the driving power reduction effect of the compression means by the ejector 15 can be obtained.

  As a result, both the compression efficiency improvement effect and the driving power reduction effect of the compression means can be sufficiently obtained, and the COP of the ejector refrigeration cycle can be effectively improved.

  Furthermore, since the saturated gas phase refrigerant can be sucked into the first compression means 11a from the gas phase refrigerant outlet of the intermediate pressure side gas-liquid separator 14, the second compression means 21a can be sucked only with the discharged refrigerant. The COP can be further improved by reducing the amount of compression work when the refrigerant is isentropically compressed in the one compression means 11a.

  The ability to effectively improve the COP as in this embodiment is that the refrigerant evaporation temperature of the suction side evaporator 19 is -30, for example, as in this embodiment, where the pressure difference between the high-pressure refrigerant and the low-pressure refrigerant is large. It is extremely effective in a refrigeration cycle apparatus that lowers to an extremely low temperature of -10 ° C.

(Second Embodiment)
In the present embodiment, an example in which an internal heat exchanger 30 is added to the ejector refrigeration cycle 100 of the first embodiment will be described as shown in the overall configuration diagram of FIG. This internal heat exchanger 30 is between the liquid phase refrigerant separated by the intermediate pressure side gas-liquid separator 14 passing through the high pressure side refrigerant flow path 30a and the low pressure side refrigerant of the cycle passing through the low pressure side refrigerant flow path 30b. Heat exchange.

  More specifically, the low-pressure side refrigerant of the cycle in the present embodiment is a refrigerant sucked into the second compression means 21 a of the compressor 10. In addition, as a specific configuration of the internal heat exchanger 30, a double-pipe heat exchanger in which an inner pipe that forms a low-pressure side refrigerant flow path 30b is arranged inside an outer pipe that forms the high-pressure side refrigerant flow path 30a. The configuration is adopted. Of course, the high-pressure side refrigerant flow path 30a may be an inner pipe and the low-pressure side refrigerant flow path 30b may be an outer pipe.

  Further, a configuration in which the refrigerant pipes forming the high-pressure side refrigerant flow path 30a and the low-pressure side refrigerant flow path 30b are brazed and joined to exchange heat may be employed. Other configurations are the same as those of the first embodiment.

  Next, the operation of the present embodiment will be described based on the Mollier diagram of FIG. In addition, the code | symbol which shows the state of the refrigerant | coolant in FIG. 4 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 described in the following embodiments.

When the ejector refrigeration cycle 100 of this embodiment is operated, the enthalpy of the gas-phase refrigerant that has flowed out of the accumulator 17 is increased by the action of the internal heat exchanger 30 with respect to the first embodiment (i ₄ points → i ' ₄ point), the enthalpy of the liquid phase refrigerant flowing out from the liquid phase refrigerant outlet of the intermediate pressure side gas-liquid separator 14 decreases (e ₄ point → e ′ ₄ point). Other operations are the same as those in the first embodiment.

  Thereby, since the dryness of the injection refrigerant injected from the nozzle part 15a can be reduced and the flow velocity of the injection refrigerant can be reduced, the refrigerant pressure flowing out from the diffuser part 15c can be reduced. Therefore, the enthalpy of the refrigerant in the accumulator 17 can be reduced, and the enthalpy of the liquid phase refrigerant flowing from the accumulator 17 to the suction side evaporator 19 can also be reduced.

  Therefore, not only can the same effect as in the first embodiment be obtained, but also the enthalpy difference between the enthalpy of the inlet side refrigerant and the enthalpy of the outlet side refrigerant of the suction side evaporator 19 can be increased, and the ejector refrigeration cycle The refrigerating capacity which 100 can exhibit can be increased. As a result, COP can be further improved.

(Third embodiment)
In the present embodiment, an example in which the configuration of the internal heat exchanger 30 is changed with respect to the ejector refrigeration cycle 100 of the second embodiment as illustrated in the overall configuration diagram of FIG. 5 will be described. More specifically, the low-pressure side refrigerant of the cycle in the present embodiment is a refrigerant that is sucked into the refrigerant suction port 15 b of the ejector 15. Other configurations are the same as those of the first embodiment.

Next, the operation of the present embodiment will be described based on the Mollier diagram of FIG. When the ejector refrigeration cycle 100 of this embodiment is operated, the enthalpy of the refrigerant flowing out from the suction side evaporator 19 is increased by the action of the internal heat exchanger 30 (l ₆ points → l ′ ₆ points), and the intermediate pressure side The enthalpy of the liquid phase refrigerant flowing out from the liquid phase refrigerant outlet of the gas-liquid separator 14 decreases (e ₆ points → e ′ ₆ points). Other operations are the same as those in the first embodiment.

  Therefore, when the ejector-type refrigeration cycle 100 of this embodiment is operated, not only the same effect as in the first embodiment can be obtained, but also the inlet-side refrigerant of the suction-side evaporator 19 can be obtained as in the second embodiment. The enthalpy difference between the enthalpy and the enthalpy of the outlet side refrigerant can be increased, and the refrigerating capacity that the ejector refrigeration cycle 100 can exhibit can be increased. As a result, COP can be further improved.

(Fourth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 7, with respect to the ejector refrigeration cycle 100 of the first embodiment, the ejector 15 outlet side (specifically, the diffuser portion 13 c outlet side) and the compressor 10. The example which has arrange | positioned the outflow side evaporator 16 between these intermediate pressure ports 10c is demonstrated.

  The basic configuration of the outflow side evaporator 16 is the same as that of the suction side evaporator 19. Further, the outflow side evaporator 16 exchanges heat between the refrigerant flowing out of the ejector 15 and the blown air blown from the blower fan 16a, thereby evaporating the refrigerant flowing out of the ejector 15 and exerting an endothermic effect. It is a vessel.

  Accordingly, in the present embodiment, the blown air blown from the blower fan 16a is also the heat exchange target fluid. The blower fan 16a 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. Other configurations are the same as those of the first embodiment.

Operating the ejector refrigerant cycle of the present embodiment, not only operate in the same manner as the first embodiment, the outflow-side evaporator 16, as shown in the Mollier diagram of FIG. 8, from ₈ point h h ' The liquid phase refrigerant in the process up to ₈ points can be evaporated to exert an endothermic effect. Thereby, the blowing air from the blowing fan 16a can also be cooled. Other operations are the same as those in the first embodiment.

  At this time, in the outflow side evaporator 16, the refrigerant evaporates at a temperature higher than the refrigerant evaporation temperature in the suction side evaporator 19. That is, in the suction side evaporator 19 and the outflow side evaporator 16, the refrigerant evaporates at different temperature zones. Thereby, in this embodiment, while being able to acquire the effect similar to 1st Embodiment, the air in the refrigerator in a refrigerator which preserve | saves food, a drink, etc. at the low temperature of 0 to 10 degreeC with the ventilation fan 16a, for example. Can also be cooled.

(Fifth embodiment)
An example in which the ejector refrigeration cycle 200 of the present invention is applied to a refrigeration / refrigeration apparatus will be described with reference to FIGS. This freezing / refrigeration apparatus cools the inside of the refrigerator, which is the cooling target space, to a low temperature of about 0 to 10 ° C., and further cools the inside of the freezer, which is another cooling target space, to an extremely low temperature of about −30 to −10 ° C. To do. FIG. 9 is an overall configuration diagram of the ejector refrigeration cycle 200 of the present embodiment.

  The ejector refrigeration cycle 200 of the present embodiment 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. is there. Therefore, in the entire configuration diagram of FIG. 9 and subsequent figures, the same reference numerals are given to the same or equivalent parts as in the first embodiment, and the description thereof is omitted.

  In the ejector-type refrigeration cycle 200, a branching section 22 that branches the flow of the intermediate pressure refrigerant flowing out from the intermediate pressure side gas-liquid separator 14 is connected to the downstream side of the liquid phase refrigerant outlet of the intermediate pressure side gas-liquid separator 14. .

  The branch portion 22 is configured by a three-way joint having three inflow / outflow ports. One of the inflow / outflow ports is a refrigerant inflow port, and two are refrigerant outflow ports. Such a three-way joint may be constituted by joining pipes having different pipe diameters, or may be constituted by providing a plurality of refrigerant passages having different passage diameters in a metal block or a resin block.

  One refrigerant outlet of the branch portion 22 is connected to the nozzle portion 15a side of the ejector 15, and the other refrigerant outlet is connected to the refrigerant suction port 15b side of the ejector 15. Further, the outlet side evaporator 16 similar to that of the fourth embodiment is connected to the outlet side of the diffuser portion 15 c of the ejector 15, and the suction port 10 b of the compressor 10 is connected to the refrigerant outlet side of the outlet side evaporator 16. It is connected.

  Further, a suction side evaporator 19 is connected to the other refrigerant outlet of the branch portion 22 via a variable throttle mechanism 18 which is a suction side pressure reducing means. A refrigerant suction port 15 b of the ejector 15 is connected to the outlet side of the suction side evaporator 19. 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. When the ejector-type refrigeration cycle 200 of this embodiment is operated, the gas-phase refrigerant that has flowed out from the gas-phase refrigerant outlet of the intermediate-pressure side gas-liquid separator 14 is, as in the first embodiment, the intermediate-pressure port 10c of the compressor 10. Through the compressor 10.

  On the other hand, the flow of the liquid-phase refrigerant flowing out from the liquid-phase refrigerant outlet of the intermediate pressure side gas-liquid separator 14 is divided into the refrigerant flow flowing into the nozzle portion 15a side of the ejector 15 and the refrigerant suction port 15b of the ejector 15 at the branch portion 22. It is divided into the refrigerant flow flowing into the side.

  Here, in this embodiment, when the refrigerant evaporation temperature of the suction-side evaporator 19 reaches a predetermined temperature, the refrigerant flow rate Gnoz flowing into the nozzle portion 15a side and the refrigerant flow rate Ge flowing into the refrigerant suction port 15b side The flow rate characteristics (pressure loss characteristics) of the nozzle unit 15a and the variable throttle mechanism 18 are determined so that the flow rate ratio Ge / Gnoz of the nozzles 15a becomes an optimum flow rate ratio that can exhibit a high COP as a whole cycle.

The intermediate-pressure refrigerant that has flowed out from the branch portion 22 toward the nozzle portion 15a flows in the order of the nozzle portion 15a → the diffuser portion 15c (e ₁₀ points → f ₁₀ points → g ₁₀ points → h ₁₀ points), and flows to the outflow side evaporator 16. Inflow.

Refrigerant flowing into the discharge side evaporator 16 evaporates by absorbing heat from the refrigerator air circulated blown by the blower fan 16a (h ₁₀ points → i ₁₀ points). Thereby, the air in a refrigerator is cooled. Then, the refrigerant flowing out from the outflow side evaporator 16 is sucked into the second compression means 21a of the compressor 10 and compressed (i ₁₀ points → m ₁₀ points).

On the other hand, the intermediate-pressure refrigerant that has flowed out from the branch portion 22 toward the refrigerant suction port 15b is further decompressed and expanded isoenthalpically by the variable throttle mechanism 18 to reduce its pressure (e ₁₀ points → k ₁₀ points). Variable decompressed and expanded refrigerant is in throttle mechanism 18, and flows into the suction side evaporator 19, the air blowing fan 19a is evaporated by absorbing heat from the freezer in air circulated blown (k ₁₀ points → l ₁₀ points). Thereby, the air in a freezer is cooled.

As described above, the refrigerant that has flowed out of the suction side evaporator 19 is sucked from the refrigerant suction port 15b (l ₁₀ points → g ₁₀ points). Other operations are the same as those in the first embodiment.

  Since the ejector refrigeration cycle 200 of this embodiment operates as described above, the inside of the refrigerator and the freezer can be cooled. That is, since the flow of the refrigerant is divided so that the flow rate ratio Ge / Gnoz becomes the optimum flow rate ratio in the branching portion 22, the refrigerant is appropriately supplied to both the outflow side evaporator 16 and the suction side evaporator 19. it can. Therefore, both the outflow side evaporator 16 and the suction side evaporator 19 can exhibit the cooling action simultaneously.

  At this time, the refrigerant evaporation pressure of the suction side evaporator 19 becomes the pressure after the pressure is reduced by the variable throttle mechanism 18 after being increased by the diffuser portion 15 c, and the refrigerant evaporation pressure of the outflow side evaporator 16 is the pressure of the suction side evaporator 19. The refrigerant evaporation pressure becomes the pressure after being increased by the second compressor 21 and the diffuser unit 15c.

  Therefore, the refrigerant evaporation pressure (refrigerant evaporation temperature) of the suction side evaporator 19 can be made sufficiently lower than the refrigerant evaporation pressure (refrigerant evaporation temperature) of the outflow side evaporator 16. As a result, the outflow evaporator 16 can be used for cooling in a low-temperature refrigerator, and the suction-side evaporator 19 can be used for cooling in a cryogenic freezer.

Further, as in the first embodiment, even if the refrigerant discharge capacities of the first and second compression units 11a and 21a are changed, the pressure loss in the refrigerant passage from the suction side evaporator 19 to the refrigerant suction port 15b of the ejector 15 is changed. Therefore, the effects of improving the compression efficiency of the compression means and the effect of reducing the driving power can be sufficiently obtained. As a result, the COP of the ejector-type refrigeration cycle can be effectively improved. Further, in this embodiment, the compressor 10 → the radiator 12 → the fixed throttle 13 → the intermediate pressure side gas-liquid separator 14 → the branch portion 22 → the ejector. 15 → Outflow side evaporator 16 → Compressor 10 in this order, and further, compressor 10 → radiator 12 → fixed throttle 13 → intermediate pressure side gas-liquid separator 14 → branching section 22 → variable throttle mechanism 18 → suction side The refrigerant flows in the order of evaporator 19 → ejector 15 → outflow side evaporator 16 → compressor 10.

  That is, since the flow of the refrigerant passing through the evaporators such as the outflow side evaporator 16 and the suction side evaporator 19 is annular, lubricating oil (refrigeration machine oil) for the first and second compressors 11 and 21 is used as the refrigerant. Even if mixed, this oil can be prevented from staying in the outflow side evaporator 16 and the suction side evaporator 19.

(Sixth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 11, the outflow-side evaporator 16 and the blower fan 16a are eliminated from the ejector refrigeration cycle 200 of the fifth embodiment, and the accumulator 17 and internal heat are further eliminated. An example in which the exchanger 30 is added will be described. Note that the ejector refrigeration cycle 200 of the present embodiment is applied to a refrigerator similar to the first embodiment.

  This internal heat exchanger 30 is between the liquid-phase refrigerant that has flowed out from the branch portion 22 that passes through the high-pressure side refrigerant flow path 30a to the variable throttle mechanism 18 side, and the low-pressure side refrigerant of the cycle that passes through the low-pressure side refrigerant flow path 30b. Heat exchange. More specifically, the low-pressure side refrigerant of the cycle in the present embodiment is a refrigerant that is sucked into the refrigerant suction port 15 b of the ejector 15.

  Of course, as in the second embodiment, the low-pressure side refrigerant of the cycle may be a refrigerant sucked into the second compression means 21a. Other configurations are the same as those of the fifth embodiment.

Next, the operation of the present embodiment will be described based on the Mollier diagram of FIG. When the ejector-type refrigeration cycle 200 of this embodiment is operated, the enthalpy of the refrigerant flowing out from the suction-side evaporator 19 is increased (l ₁₂ points → l ′ ₁₂ points), the enthalpy of the liquid phase refrigerant flowing out from the liquid phase refrigerant outlet of the intermediate pressure side gas-liquid separator 14 decreases (e ₁₂ → e ′ ₁₂ points).

Further, refrigerant flowing from the diffuser portion 15c of the ejector 15, since the discharge side evaporator 16 is discontinued, the gas-liquid separation flows into the accumulator 17 (h ₁₂ points → i ₁₂ points). Then, the gas-phase refrigerant separated by the accumulator 17 is sucked into the second compression means 21 a of the compressor 10. Other operations are the same as those in the fifth embodiment.

  Therefore, when the ejector refrigeration cycle 200 of the present embodiment is operated, the inside of the freezer can be cooled by the heat absorbing action of the refrigerant in the suction side evaporator 19. Further, similarly to the first embodiment, the effects of both the compression efficiency improvement effect and the driving power reduction effect of the compression means can be sufficiently obtained, and the COP of the ejector refrigeration cycle can be effectively improved.

  Furthermore, the enthalpy of the refrigerant flowing into the suction side evaporator 19 can be reduced by the action of the internal heat exchanger 30 with respect to the fifth embodiment. Therefore, since the enthalpy difference between the enthalpy of the inlet side refrigerant and the enthalpy of the outlet side refrigerant of the suction side evaporator 19 can be increased to increase the refrigeration capacity, the COP can be further improved.

  In addition, in the present embodiment, in the internal heat exchanger 30, heat exchange is performed between the high-pressure refrigerant flowing through the refrigerant passage extending from the branch portion 22 outlet side to the variable throttle mechanism 18 inlet side and the low-pressure refrigerant sucked into the refrigerant suction port 15b. Therefore, the enthalpy of the refrigerant flowing into the nozzle portion 15a from the branch portion 22 is not unnecessarily reduced.

  Thereby, the further COP improvement effect can be acquired. The reason is that the amount of recovered energy in the nozzle portion 15a can be increased by unnecessarily reducing the enthalpy of the refrigerant flowing into the nozzle portion 15a.

  This will be described in more detail. As the enthalpy of the refrigerant flowing into the nozzle portion 15a increases, the slope of the isentropic line becomes gentle (small). Therefore, when the nozzle portion 15a is isentropically expanded by the same pressure, the higher the enthalpy of the nozzle portion 15a inlet-side refrigerant, the higher the enthalpy of the nozzle portion 15a inlet-side refrigerant and the enthalpy of the nozzle portion 15a outlet-side refrigerant. The difference (recovered energy amount) increases.

  Therefore, as the enthalpy of the refrigerant flowing into the nozzle portion 15a increases, the amount of recovered energy in the nozzle portion 15a increases. As the amount of recovered energy increases, the amount of pressure increase in the diffuser portion 15c can be increased, and a further COP improvement effect can be obtained.

(Seventh embodiment)
An example in which the ejector refrigeration cycle 300 of the present invention is applied to the same refrigeration / refrigeration apparatus as in the fifth embodiment will be described with reference to FIGS. FIG. 13 is an overall configuration diagram of an ejector refrigeration cycle 300 of the present embodiment.

  In the ejector refrigeration cycle 300, as shown in FIG. 13, the accumulator 17 is abolished with respect to the fourth embodiment, and the flow of the refrigerant flowing out of the diffuser portion 15c is branched to the outlet side of the diffuser portion 15c of the ejector 15. A branch portion 32 is provided.

  The basic configuration of the branch unit 32 is the same as that of the branch unit 22 of the fifth embodiment. This branch part 32 branches the flow of the refrigerant that has flowed out of the diffuser part 15c, and flows it out to the outflow side evaporator 16 side and the variable throttle mechanism 18 side. In the present embodiment, the inlet side of the suction side evaporator 19 is connected to the outlet side of the variable throttle mechanism 18.

  Further, the branch portion 32 has a flow direction of the refrigerant flowing out from the one refrigerant outlet 32b to the outflow side evaporator 16 side, and a flow direction of the refrigerant flowing out from the other refrigerant outlet 32c to the variable throttle mechanism 18 side. In addition, it is formed in a substantially Y shape 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 inflow port 32a from the diffuser portion 15c outlet side.

  Therefore, the refrigerant that has flowed into the branch portion 32 flows out of the branch portion 32 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 15 at the branch portion 32 is maintained. Of course, the branch portion 32 is not limited to this, and may be formed in a substantially T-shape or the like.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. When the ejector refrigeration cycle 300 according to the present embodiment is operated, the refrigerant flowing out of the diffuser unit 15c causes the refrigerant flowing into the outflow side evaporator 16 side and the refrigerant flowing into the variable throttle mechanism 18 side at the branching unit 32. Divided into flow.

  Here, in this embodiment, the refrigerant flowing into the outflow side evaporator 16 side is set by setting the refrigerant passage area on the refrigerant outlet 32b side of the branch portion 32 larger than the refrigerant passage area on the refrigerant outlet 32c side. The flow rate G1 is set to be larger than the refrigerant flow rate G2 flowing into the variable throttle mechanism 18 side.

Refrigerant flowing from the branch portion 32 to the discharge side evaporator 16 evaporates by absorbing heat from the refrigerator air circulated blown by the blower fan 16a (h ₁₄ points → i ₁₄ points). Thereby, the air in a refrigerator is cooled. Then, the refrigerant flowing out of the outflow side evaporator 16 is sucked into the second compression means 21a of the compressor 10, and is compressed and pressurized until it reaches an intermediate pressure (i ₁₄ point → m ₁₄ point).

On the other hand, the refrigerant flowing into the variable throttle mechanism 18 from the branch portion 32 is further decompressed and expanded in an isenthalpy manner to reduce its pressure (h ₁₄ point → k ₁₄ point). Variable decompressed and expanded refrigerant is in throttle mechanism 18, and flows into the suction side evaporator 19, absorbs heat from the freezer in air circulated blown by the blower fan 19a to evaporate (k ₁₄ points → l ₁₄ points). Thereby, the air in a freezer is cooled.

The refrigerant that has flowed out of the suction side evaporator 19 is sucked into the ejector 15 from the refrigerant suction port 15b ( ₁₄ points → g ₁₄ points). Other operations are the same as those in the fourth embodiment.

  As in the fifth embodiment, the ejector refrigeration cycle 300 of the present embodiment uses the outflow side evaporator 16 for cooling in a low-temperature refrigerator and the suction-side evaporator 19 for cooling in a cryogenic freezer. Can be used. Further, similarly to the first embodiment, the effects of both the compression efficiency improvement effect and the driving power reduction effect of the compression means can be sufficiently obtained, and the COP of the ejector refrigeration cycle can be effectively improved.

  Furthermore, since the refrigerant flow rate G1 flowing from the branch part 32 to the outflow side evaporator 16 side becomes larger than the refrigerant flow rate G2 flowing from the branch part 32 to the variable throttle mechanism 18 side, more refrigerant is supplied. Heat can be dissipated by the radiator 12. Thereby, the endothermic amount of the refrigerant, that is, the refrigerating capacity of the cycle can be expanded as a whole cycle, and the COP can be further improved.

(Eighth embodiment)
An example in which the ejector refrigeration cycle 400 of the present invention is applied to the same refrigeration / refrigeration apparatus as in the fifth embodiment will be described with reference to FIGS. FIG. 15 is an overall configuration diagram of the ejector refrigeration cycle 400 of the present embodiment.

  In the ejector-type refrigeration cycle 400, as shown in FIG. 15, a first branching portion that branches the flow of the liquid-phase refrigerant flowing out from the intermediate-pressure side gas-liquid separator 14 to the liquid-phase refrigerant outlet of the intermediate-pressure side gas-liquid separator 14 22 is connected. The basic configuration of the first branch portion 22 is the same as that of the branch portion 22 of the fifth embodiment.

  The nozzle portion 15a of the ejector 15 is connected to one refrigerant outlet of the first branch portion 22, and the first variable throttle mechanism 18 side as the first suction side pressure reducing means is connected to the other refrigerant outlet. Yes.

  Further, the refrigerant inlet 32 a of the second branch portion 32 is connected to the outlet side of the diffuser portion 15 c of the ejector 15. The basic configuration of the second branch part 32 is the same as that of the branch part 32 of the seventh embodiment. The refrigerant outlet 32b of the second branch portion 32 is connected to the outflow side evaporator 16 and the other refrigerant outlet 32c is connected to the second variable throttle mechanism 28 as the second suction side pressure reducing means. Yes.

  The basic configuration of the first and second variable aperture mechanisms 18 and 28 is the same as that of the variable aperture mechanism 18 of the first embodiment. Furthermore, the first and second variable throttle mechanisms 18 and 28 of the present embodiment can fully close their throttle openings.

  Therefore, when the first variable throttle mechanism 18 fully closes the throttle passage, the flow of the liquid-phase refrigerant that has flowed out of the intermediate pressure side gas-liquid separator 14 is not branched at the first branching section 22, but its total flow rate. Flows out to the ejector 15 side. Further, when the second variable throttle mechanism 28 fully closes the throttle passage, the flow of the refrigerant flowing out from the diffuser portion 15c is not branched at the second branch portion 32, and the total flow rate is reduced to the outflow side evaporator 16. To the side.

  The outlet side of the first and second variable throttle mechanisms 18, 28 is connected to a merging portion 20 that joins the refrigerant flows that have flowed out of the first and second variable throttle mechanisms 18, 28. The basic configuration of the merging unit 20 is the same as that of the second branch unit 32. That is, in the junction part 20, two out of the three inflow / outflow ports 20a to 20c are the refrigerant inflow ports 20b and 20c, and one is the refrigerant outflow port 20a.

  More specifically, in the merging portion 20 of the present embodiment, the flow direction of the refrigerant flowing from the first variable throttle mechanism 18 into the one refrigerant inlet 20b, and the other refrigerant inlet from the second variable throttle mechanism 28. The flow direction of the refrigerant flowing into 20c is formed in a substantially Y shape so as to face the target direction and intersect at an acute angle with respect to the flow direction of the refrigerant flowing out from the refrigerant outlet 20a to the suction side evaporator 19. .

  Therefore, the refrigerant that has flowed into the merging portion 20 flows out of the merging portion 20 without unnecessarily reducing the flow velocity when the flows are merged. Thereby, the flow velocity (dynamic pressure) of the refrigerant that has flowed out of the first and second electric expansion valves 19 and 29 is maintained in the merging portion 20. A suction-side evaporator 19 is connected to the refrigerant outlet 20 a of the junction 20. Other configurations are the same as those of the fifth embodiment.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. Here, in the ejector-type refrigeration cycle 400 of the present embodiment, the control device controls the first and second variable throttle mechanisms 18 and 28 to the throttle state or the fully closed state, so that the following three types of cycle configurations are configured. Can be realized.

  When the control device places the first variable throttling mechanism 18 in the fully closed state and the second variable throttling mechanism 28 in the throttling state, it is possible to realize a cycle configuration in which the refrigerant flow is branched only by the second branching portion 28 (hereinafter, The operation mode in this cycle configuration is called the low pressure branch operation mode). The operation in this low-pressure branch operation mode is the same as in the seventh embodiment.

  When the control device places the first variable throttling mechanism 18 in the throttling state and the second variable throttling mechanism 28 in the fully closed state, it is possible to realize a cycle configuration in which the flow of the refrigerant is branched only by the first branching portion 22 (hereinafter referred to as “the first variable throttling mechanism”). The operation mode in this cycle configuration is called a high-pressure branch operation mode). The operation in the high-pressure branch operation mode is the same as that in the fifth embodiment.

  When the control device places both the first and second electric expansion valves 19 and 29 in the throttle state, it is possible to realize a cycle configuration in which the refrigerant flow is branched at the same time in the first branch portion 22 and the second branch portion 28 (hereinafter referred to as the following). The operation mode in this cycle configuration is called the simultaneous branch operation mode). The operation of this simultaneous branch operation mode will be described later.

  Moreover, each said operation mode is switched based on the refrigerating capacity or external temperature required for a cycle. In this embodiment, at normal load where normal refrigeration capacity is required, the mode is switched to the low pressure branch operation mode, which requires higher refrigeration capacity than at normal load, and the flow rate of refrigerant circulating in the cycle is higher than at normal load. When the load is high, switch to the high-pressure branch operation mode.

  In addition, the refrigeration capacity is not required more than during normal load, and the flow rate of refrigerant circulating in the cycle is lower than during normal load, or when the outside air temperature is lower than a predetermined reference temperature, the cycle When the difference between the high pressure and the low pressure becomes smaller than a predetermined pressure difference, the simultaneous branching operation mode is switched.

Here, the operation in the simultaneous branching mode will be described based on the Mollier diagram of FIG. In the simultaneous branching operation mode, the flow of the liquid-phase refrigerant flowing out from the liquid-phase refrigerant outlet of the intermediate pressure side gas-liquid separator 14 flows to the first branch portion 22 (point e _{16 in} FIG. 16), as in the fifth embodiment. Thus, the refrigerant flow is divided into a refrigerant flow flowing into the nozzle portion 15a side of the ejector 15 and a refrigerant flow flowing into the refrigerant suction port 15b side.

  The gas phase refrigerant flowing out from the gas phase refrigerant outlet of the intermediate pressure side gas-liquid separator 14 flows into the compressor 10 through the intermediate pressure port 10c of the compressor 10 as in the fifth and seventh embodiments. On the other hand, the flow of the liquid-phase refrigerant flowing out from the liquid-phase refrigerant outlet of the intermediate pressure side gas-liquid separator 14 flows into the nozzle portion 15a side of the ejector 15 at the first branch portion 22 as in the fifth embodiment. The refrigerant flow is divided into a refrigerant flow and a refrigerant flow flowing into the refrigerant suction port 15b of the ejector 15.

The intermediate pressure refrigerant that has flowed out from the first branch portion 22 toward the nozzle portion 15a flows in the order of the nozzle portion 15a → the diffuser portion 15c (e ₁₆ point → f ₁₆ point → g ₁₆ point → h ₁₆ point). On the other hand, intermediate-pressure refrigerant flowing from the first branch portion 22 to the refrigerant suction port 15b side, the variable throttle is further isenthalpic depressurize expanded by mechanism 18, it reduces the pressure (e ₁₆ points → ka ₁₆ points ).

The refrigerant that has flowed out of the diffuser portion 15c is split in the second branch portion 32 into a refrigerant flow that flows into the outflow side evaporator 16 side and a refrigerant flow that flows into the second variable throttle mechanism 28 side. Refrigerant flowing into the discharge side evaporator 16 from the second branch portion 32, the blower fan 16a is evaporated by absorbing heat from the circulation blower has been refrigerator air (h ₁₆ points → i ₁₆ points). Thereby, the air in a refrigerator is cooled.

On the other hand, the refrigerant flowing into the second variable throttle mechanism 18 from the second branch portion 32 is further decompressed and expanded in an isenthalpy manner to reduce its pressure (h ₁₆ point → kβ ₁₆ point). The refrigerant decompressed and expanded by the second variable throttle mechanism 28 merges with the refrigerant decompressed by the first variable throttle mechanism 18 at the junction 20 (kβ ₁₆ points → kγ ₁₆ points and kα ₁₆ points). → kγ ₁₆ points).

The refrigerant that has flowed out of the merging portion 20 flows into the suction-side evaporator 19, absorbs heat from the freezer air circulated by the blower fan 19a, and evaporates (kγ ₁₆ points → l ₁₆ points). Thereby, the air in a freezer is cooled. Then, the refrigerant flowing out from the suction side evaporator 19 is sucked into the ejector 15 from the refrigerant suction port 15b (l ₁₆ points → g ₁₆ points). Other operations are the same as those in the fifth and seventh embodiments.

  Since the ejector refrigeration cycle 400 of this embodiment operates as described above, the same effects as those of the seventh embodiment can be obtained in the low-pressure branch mode. In the high-pressure branch mode, the same effect as that of the fifth embodiment can be obtained.

  Further, in the simultaneous branching mode, the outflow side evaporator 16 can be used for cooling in the low-temperature refrigerator, the suction side evaporator 19 can be used for cooling in the cryogenic freezer, and the compression efficiency of the compression means can be used. It is possible to sufficiently improve both the improvement effect and the driving power reduction effect, and to effectively improve the COP of the ejector refrigeration cycle.

  Further, in the simultaneous branching operation mode, it is possible to realize a cycle configuration in which the refrigerant flowing out from both the first variable throttle mechanism 18 and the second variable throttle mechanism 28 is supplied to the suction side evaporator 19. Accordingly, the refrigerant supplied to the suction-side evaporator 19 with respect to the cycle configuration in which the refrigerant flowing out from one of the first variable throttle mechanism 18 and the second variable throttle mechanism 28 is supplied to the suction-side evaporator 19. It becomes easy to increase the flow rate.

(Ninth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 17, the arrangement of the branch portion 22 is changed with respect to the ejector refrigeration cycle 200 of the fifth embodiment, and further, the refrigerant flow downstream of the branch portion 22. An example in which an auxiliary radiator 12e that dissipates heat from the refrigerant flowing into the fixed throttle 13 is provided will be described.

  More specifically, the branch part 22 of this embodiment is arrange | positioned at the heat radiator 12 exit side, and branches the flow of the refrigerant | coolant which flowed out from the heat radiator 12. FIG. And the nozzle part inlet side of the ejector 15 is connected to one refrigerant | coolant outlet of the branch part 22, and the auxiliary | assistant heat radiator 12e inlet side is connected to the other refrigerant | coolant outlet.

  The auxiliary radiator 12e heat-exchanges the high-pressure refrigerant that has flowed out of the radiator 12 and the outside air (outside air) blown by the cooling fan 12a to further radiate and cool the high-pressure refrigerant. It is. Moreover, the heat radiator 12 of this embodiment is reducing the heat exchange capability by reducing a heat exchange area with respect to the above-mentioned embodiment.

  In FIG. 17, the cooling fan 12a is disposed in the vicinity of the radiator 12 for clarity of illustration, but the cooling fan 12a also blows outside air to the auxiliary radiator 12e. Of course, the outside air may be blown to the radiator 12 and the auxiliary radiator 12e from independent blowing fans. Other configurations are the same as those of the fifth embodiment.

Next, the operation of the present embodiment will be described based on the Mollier diagram of FIG. When the ejector refrigeration cycle 200 of the present embodiment is operated, the refrigerant discharged from the first compression means 11a of the compressor 10 dissipates heat and condenses in the radiator 12 as in the first embodiment, and the gas is condensed. It will be in a liquid two-phase state (a ₁₈ points → b ₁₈ points). This is because the heat exchange capability of the radiator 12 is reduced compared to the fifth embodiment described above.

  The high-pressure refrigerant that has flowed out of the radiator 12 flows into the branch portion 22 and is divided into a refrigerant flow that flows into the nozzle portion 15 a side of the ejector 15 and a refrigerant flow that flows into the refrigerant suction port 15 b side of the ejector 15.

As in the fifth embodiment, the refrigerant that has flowed from the branch portion 22 to the nozzle portion 15 side of the ejector 15 flows in the order of the nozzle portion 15a of the ejector 15 → the diffuser portion 15c → the outflow side evaporator 16. 2. The air is sucked into the compression means 21a, and is compressed and pressurized until it reaches an intermediate pressure (b ₁₈ point → f ₁₈ point → g ₁₈ point → h ₁₈ point → i ₁₈ point → m ₁₈ point).

On the other hand, the high-pressure refrigerant that has flowed out from the branch portion 22 to the refrigerant suction port 15b side is further cooled by the auxiliary radiator 12e and enters a liquid phase state (b ₁₈ point → b ′ ₁₈ point). The refrigerant flowing out from the auxiliary radiator 12e flows in the order of the fixed throttle 13 → the intermediate pressure side gas-liquid separator 14 → the variable throttle mechanism 18 → the suction side evaporator 19 and sucks the refrigerant in the ejector 15 as in the fifth embodiment. It is sucked from the mouth 15b (b ′ ₁₈ points → c ₁₈ points → e ₁₈ points → k ₁₈ points → l ₁₈ points → g ₁₈ points).

  Therefore, when the ejector refrigeration cycle 200 of the present embodiment is operated, the same effect as that of the fifth embodiment can be obtained. Furthermore, since the heat exchange capability of the radiator 12 is reduced, the enthalpy of the refrigerant flowing into the nozzle portion 15a is not unnecessarily reduced. Therefore, the COP improvement effect by not reducing the enthalpy of the refrigerant | coolant which flows in into the nozzle part 15a similarly to 6th Embodiment can be acquired.

  Further, since the refrigerant that has flowed out of the radiator 12 directly flows into the nozzle portion 15a of the ejector 15, the amount of pressure reduction in the nozzle portion 15a of the ejector 15, that is, the pressure between the nozzle portion 15a inlet side pressure and the nozzle portion 15a outlet side pressure. The pressure difference increases. Thereby, the difference between the enthalpy of the refrigerant on the inlet side of the nozzle portion 15a and the enthalpy of the refrigerant on the outlet side of the nozzle portion 15a can be increased to increase the amount of recovered energy, and COP can be further improved.

(10th Embodiment)
In the present embodiment, an example in which an internal heat exchanger 31 is added to the ejector refrigeration cycle 200 of the fifth embodiment will be described as shown in the overall configuration diagram of FIG. The internal heat exchanger 31 includes a refrigerant in a decompression / expansion process passing through a fixed throttle 18a serving as a suction-side decompression unit constituting the high-pressure side refrigerant flow path, and a second compression of the compressor 10 passing through the low-pressure side refrigerant flow path 31b. Heat is exchanged with the refrigerant sucked by the means 21a.

  As a specific configuration of the internal heat exchanger 31, 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 forming the low-pressure side refrigerant flow path 31b. Adopted. Of course, a configuration in which heat is exchanged by brazing the fixed throttle 18a and the refrigerant pipe forming the low-pressure side refrigerant flow path 31b may be employed.

  Further, when the variable throttle mechanism 18 is employed as the suction side pressure reducing means, the heat exchange is performed by brazing the refrigerant pipe forming the low pressure side refrigerant flow path 31b to the outer peripheral surface of the throttle passage of the variable throttle mechanism 18. Can be adopted. Other configurations are the same as those of the fifth embodiment.

Next, the operation of the present embodiment will be described based on the Mollier diagram of FIG. When the ejector refrigeration cycle 200 of this embodiment is operated, the second compression means 21a suction of the second compression means 21a suction-side refrigerant of the compressor 10 is compared with the fifth embodiment by the action of the internal heat exchanger 31. The enthalpy of the side refrigerant increases (i ₂₀ point in FIG. 20 → i ′ ₂₀ point), and the enthalpy of the decompression and expansion process in the fixed throttle 18a decreases (e ₂₀ point → k ₂₀ point).

  In other words, the refrigerant passing through the fixed throttle 18a is cooled to the temperature of the refrigerant sucked by the second compression means 21a while expanding under reduced pressure, and the enthalpy is reduced. Thereby, compared with 1st Embodiment, the enthalpy of the refrigerant | coolant which flows in into the outflow side evaporator 16 and the suction side evaporator 19 can be decreased. Other operations are the same as those in the fifth embodiment.

  Therefore, when the ejector refrigeration cycle 200 of the present embodiment is operated, the same effect as that of the fifth embodiment can be obtained. Furthermore, the enthalpy of the refrigerant flowing into the suction side evaporator 19 can be reduced by the action of the internal heat exchanger 31 with respect to the fifth embodiment. Thereby, the enthalpy difference between the enthalpy of the inlet-side refrigerant and the enthalpy of the outlet-side refrigerant of the suction-side evaporator 19 is increased to increase the refrigeration capacity, and the COP can be further improved.

(Eleventh embodiment)
An example in which the ejector refrigeration cycle 500 of the present invention is applied to the same refrigeration / refrigeration apparatus as in the fifth embodiment will be described with reference to FIGS. FIG. 21 is an overall configuration diagram of an ejector refrigeration cycle 500 of the present embodiment.

  In the ejector-type refrigeration cycle 500, as shown in FIG. 21, a branch portion 22 similar to that of the fifth embodiment is connected to the discharge port side of the compressor 10. The first radiator 121 is connected to one refrigerant outlet of the branch portion 22, and the second radiator 122 is connected to the other refrigerant outlet.

  The first radiator 121 heat-exchanges the high-pressure refrigerant that has flowed out from one refrigerant outlet of the branch portion 22 and the outside air (outside air) blown by the cooling fan 121a to dissipate the high-pressure refrigerant and cool it. It is a heat exchanger for heat dissipation. The second radiator 122 heat-exchanges the high-pressure refrigerant that has flowed out from the other refrigerant outlet of the branching portion 22 and the outside air (outside air) blown by the cooling fan 122a to radiate the high-pressure refrigerant. It is a heat exchanger for heat dissipation that cools.

  Further, in the present embodiment, the heat exchange area (heat radiation performance) of the first radiator 121 is reduced by reducing the heat exchange area of the first radiator 121 with respect to the second radiator 122. It is lower than the heat exchange capacity. The cooling fans 121a and 122a are electric blowers in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the control device.

  In addition, the nozzle portion 15 a of the ejector 15 is connected to the outlet side of the first radiator 121, and the fixed throttle 13 is connected to the outlet side of the second radiator 122. Other configurations are the same as those of the fifth embodiment.

Next, the operation of the present embodiment will be described based on the Mollier diagram of FIG. Operating the refrigerant cycle 500 of the present embodiment, the refrigerant discharged from the first compression means 11a of the compressor 10 (a ₂₂ point in FIG. 22) flows into the branch portion 22, the first radiator 121 The refrigerant flow that flows into the side and the refrigerant flow that flows into the second radiator 122 side are divided.

  Here, in this embodiment, the flow rate ratio Gr1 / Gr2 between the refrigerant flow rate Gr1 flowing into the first radiator 121 side and the refrigerant flow rate Gr2 flowing into the second radiator 122 side can exhibit a high COP as a whole cycle. The passage areas (pressure loss characteristics) of the respective refrigerant passages in the branch portion 22 are determined so as to obtain the optimum flow rate ratio.

Refrigerant flowing into the first radiator 121 side, the cooling blower has been blown air from the fan 121a and (outside air) and the heat exchanger to be condensed radiator (a ₂₂ point → b1 ₂₂ points). On the other hand, the refrigerant that has flowed into the second radiator 122 side exchanges heat with the blown air (outside air) blown from the cooling fan 122a to dissipate heat and condense (a ₂₂ points → b _{22 22} points).

  At this time, since the heat exchange capability of the first radiator 121 is set lower than the heat exchange capability of the second radiator 122, the enthalpy of the refrigerant flowing out from the first radiator 121 is the second radiator 122. It becomes larger than the enthalpy of the refrigerant that has flowed out.

The refrigerant that has flowed out of the first radiator 121 flows in the order of the nozzle portion 15a of the ejector 15 → the diffuser portion 15c → the outflow side evaporator 16 and is sucked into the second compression means 21a of the compressor 10 as in the fifth embodiment. is and is compressed to an intermediate pressure is boosted (b1 ₂₂ points → f ₂₂ points → g ₂₂ points → h ₂₂ points → i ₂₂ points → m ₂₂ points).

On the other hand, the refrigerant flowing out of the second radiator 122 flows in the order of the fixed throttle 13 → the intermediate pressure side gas-liquid separator 14 → the variable throttle mechanism 18 → the suction side evaporator 19 and is sucked from the refrigerant suction port 15 b of the ejector 15. that (b2 ₂₂ points → c ₂₂ points → e ₂₂ points → k ₂₂ points → l _22-point → g ₂₂ points). Other operations are the same as those in the fifth embodiment.

  Therefore, when the ejector refrigeration cycle 200 of the present embodiment is operated, the same effect as that of the fifth embodiment can be obtained.

  Furthermore, since the heat dissipation performance of the first radiator 121 and the second radiator 122 can be changed independently, for example, the heat dissipation performance of the second radiator 122 and the heat absorption performance of the suction side evaporator 19 are easily adapted. And the heat dissipation performance of the first and second radiators 121 and 122 and the heat absorption performance of the outflow side evaporator 16 can be easily adapted. Therefore, it is easy to stabilize the operation of the cycle.

  Moreover, since the heat exchange capability of the first radiator 121 is lower than the heat exchange capability of the second radiator 122, the enthalpy of the refrigerant flowing into the nozzle portion 15a of the ejector 15 is unnecessarily reduced. You can avoid that. Therefore, the COP improvement effect by not reducing the enthalpy of the refrigerant | coolant which flows in into the nozzle part 15a similarly to 6th Embodiment can be acquired.

  Furthermore, since the refrigerant that has flowed out of the first radiator 121 directly flows into the nozzle portion 15a of the ejector 15, the reduced pressure amount in the nozzle portion 15a of the ejector 15, that is, the pressure on the nozzle portion 15a inlet side and the pressure on the nozzle portion 15a outlet side The pressure difference between becomes larger. As a result, as in the ninth embodiment, the amount of recovered energy in the ejector 15 can be increased to further improve the COP.

(Twelfth embodiment)
In this embodiment, an example in which a bypass passage 25 and an on-off valve 26 are added to the ejector refrigeration cycle 100 of the first embodiment will be described as shown in the overall configuration diagram of FIG.

  The bypass passage 25 is a refrigerant flow path that guides the high-pressure refrigerant discharged from the first compression means 11a of the compressor 10 directly to the suction-side evaporator 19, bypassing the radiator 12, and the compressor 10 and the radiator. 12 and a refrigerant pipe connecting the variable throttle mechanism 18 and the suction-side evaporator 19.

  The opening / closing valve 26 is an opening / closing means for opening / closing the bypass passage 25 and is an electromagnetic valve whose opening / closing operation is controlled by a control signal output from the control device. Furthermore, the refrigerant passage area when the on-off valve 26 is opened is smaller than the refrigerant passage area of the bypass passage 25. Accordingly, the refrigerant flowing through the bypass passage 25 is decompressed when passing through the on-off valve 26.

  The reason why the on-off valve 26 having a pressure reducing function is adopted as the on / off valve 26 is that not only the pressure difference between the pressure of the inlet side refrigerant and the pressure of the outlet side refrigerant is secured, but also the compressor This is because if the high-pressure refrigerant discharged from 10 is directly flowed into the suction-side evaporator 19, there is a concern that the refrigerant pressure in the suction-side evaporator 19 may exceed the pressure resistance of the suction-side evaporator 19.

  Therefore, in the present embodiment, the refrigerant passage area of the on-off valve 26 is formed small, and the pressure of the refrigerant flowing into the suction side evaporator 19 is lowered until it becomes lower than the pressure resistance capability of the suction side evaporator 19. .

  Therefore, when the on-off valve 26 having no pressure reducing function is arranged in the bypass passage 25, it is desirable to arrange the bypass passage side pressure reducing means in the bypass passage 25. As the bypass passage side pressure reducing means, a fixed throttle mechanism composed of a capillary tube, an orifice or the like can be adopted.

  Next, the operation of this embodiment in the above configuration will be described. In the ejector refrigeration cycle 100 of the present embodiment, it is possible to switch between a normal operation mode in which the interior is cooled and a defrost operation mode in which the suction side evaporator 19 is defrosted. In the normal operation mode, the control device closes the on-off valve 26. As a result, the operation is exactly the same as in the first embodiment.

  In the defrosting operation mode, the control device stops the operation of the cooling fan 12a, makes the variable throttle mechanism 18 fully closed, and opens the on-off valve 26. Thereby, the high-temperature refrigerant discharged from the first compression means 11 a of the compressor 11 flows into the bypass passage 25.

  At this time, in this embodiment, the pressure loss of the refrigerant circuit circulating in the order of the compressor 10 → the radiator 12 → the fixed throttle 13 → the intermediate pressure side gas-liquid separator 14 → the ejector 15 → the accumulator 17 → the compressor 10. Since the pressure loss of the refrigerant circuit circulating in the order of the compressor 10 → the bypass passage 25 → the suction side evaporator 19 → the ejector 15 → the accumulator 17 → the compressor 10 is set small, the refrigerant discharged from the compressor 10 Most of the liquid flows into the bypass passage 25.

  Of course, a three-way valve is arranged at the inlet side connection part or the outlet side connection part of the bypass passage 25, and in the normal operation mode, the refrigerant discharged from the compressor 10 is allowed to flow out only to the radiator 12 side, and the defrosting operation is performed. In the mode, the refrigerant flow path may be switched so that the refrigerant discharged from the compressor 10 flows out only to the bypass passage 25 side.

  In addition, a normal auxiliary opening / closing valve not having a pressure reducing function is arranged in the refrigerant passage extending from the inlet side connection portion of the bypass passage 25 to the inlet side of the radiator 12, and the auxiliary opening / closing valve is opened in the normal operation mode. In the defrosting operation mode, the refrigerant flow path may be switched by closing the auxiliary on-off valve.

The high-temperature and high-pressure refrigerant that has flowed into the bypass passage 25 is decompressed and expanded in an enthalpy manner when passing through the on-off valve 26 (o ₂₄ point → p ₂₄ point). The high-temperature and low-pressure gas-phase refrigerant that has passed through the on-off valve 26 flows into the suction-side evaporator 19 without flowing into the accumulator 17 side because the throttle opening of the variable throttle mechanism 18 is fully closed.

Refrigerant flowing into the suction side evaporator 19, to radiate the heat to the suction side evaporator 19 (p ₂₄ points → Q ₂₄ points). As a result, the suction side evaporator 19 is defrosted. The refrigerant radiated by the suction side evaporator 19 is depressurized by the pressure loss when passing through the refrigerant suction port 13b → the diffuser portion 15c → the accumulator 17 of the ejector (q ₂₄ points → r ₂₄ points). The gas-phase refrigerant flowing out of the accumulator 17 is sucked into the compressor 10 and compressed again (r ₂₄ point → o ₂₄ point).

  As described above, in the normal operation mode of this embodiment, the same effect as that of the first embodiment can be obtained. In the defrosting operation mode, the suction side evaporator 19 can be defrosted.

  In this embodiment, the variable throttle mechanism 18 is employed as the suction side pressure reducing means, and the throttle opening of the variable throttle mechanism 18 is fully closed during the defrosting operation. Of course, a fixed throttle is used as the suction side pressure reducing means. And a check valve that is disposed between the outlet side of the suction side pressure reducing means and the connection portion of the bypass passage 25 and allows only the refrigerant to flow from the suction side pressure reducing means side to the suction side evaporator 19 side. May be provided.

(13th Embodiment)
Next, a thirteenth embodiment of the present invention will be described with reference to FIG. In the present embodiment, the ejector refrigeration cycle of the present invention is applied to a cold storage. FIG. 25 is an overall configuration diagram of the ejector refrigeration cycle 600 of the present embodiment.

  The ejector refrigeration cycle 600 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. 5 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 600 of the present embodiment, the first electric four-way valve 51 is connected to the discharge port (discharge port 10d) of the first compression means 11a of the compressor 10. The first electric four-way valve 51 is a refrigerant flow switching means whose operation is controlled by a control signal output from the control device.

  Specifically, the first electric four-way valve 51 is provided between the discharge port 10d side of the compressor 10 and the outdoor heat exchanger 53 inlet side, the variable throttle mechanism 18 outlet side, and the use side heat exchanger 54 inlet side. Between the refrigerant flow path (circuit indicated by the solid line arrow in FIG. 25), the compressor 10 discharge port 10d side and the use side heat exchanger 54 inlet side, and the variable throttle mechanism 18 outlet side and outdoor heat. The refrigerant flow path (circuit shown by the broken line arrow in FIG. 5) that connects the inlet side of the exchanger 53 at the same time is switched.

  An outdoor heat exchanger 53 is connected to the discharge port 10d of the compressor 10 in the cooling operation mode via the first electric four-way valve 51 as in the refrigerant flow path indicated by the solid line arrow in FIG. The outdoor heat exchanger 53 is a heat exchanger that exchanges heat between the refrigerant passing through the inside and the outdoor air 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.

  Further, a second electric four-way valve 52 is connected to the outlet side of the outdoor heat exchanger 53 in the cooling operation mode. The second electric four-way valve 52 is refrigerant flow switching means whose operation is controlled by a control signal output from the control device, and the basic configuration is the same as that of the first electric four-way valve 51. is there.

  Specifically, the second electric four-way valve 52 is a refrigerant between the outlet side of the outdoor heat exchanger 53 and the inlet side of the fixed throttle 13 which is a high pressure side pressure reducing means, and the refrigerant on the outlet side of the use side heat exchanger 54 and the ejector 15. A refrigerant flow path (a circuit indicated by a solid line arrow in FIG. 25) that connects the suction port 15b at the same time, between the outdoor heat exchanger 53 outlet side and the refrigerant suction port 15b, and on the use side heat exchanger 54 outlet side The refrigerant flow path (circuit indicated by the broken line arrow in FIG. 25) that connects the fixed throttle 13 at the same time is switched.

  The use-side heat exchanger 54 is a heat exchanger that exchanges heat between the refrigerant passing through the inside and the indoor blown air that is the heat exchange target fluid 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.

  The variable throttle mechanism 18 of the present embodiment is disposed between the liquid refrigerant outlet side of the accumulator 17 and the first electric four-way valve 51. 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 ejector refrigeration cycle 600 of the present embodiment, a cooling operation mode for cooling the internal air and a heating operation mode for heating the internal air can be switched.

  The cooling operation mode is executed when the cooling operation mode is selected by the operation switch of the operation panel. In the cooling operation mode, the control device operates the first and second electric motors 11b and 21b and the blower fans 53a and 54a.

  Further, the control device simultaneously connects between the discharge port 10d side of the compressor 10 and the outdoor heat exchanger 53 inlet side, and between the variable throttle mechanism 18 outlet side and the use side heat exchanger 54 inlet side. The first electric four-way valve 51 is switched so that the connection between the outdoor heat exchanger 53 outlet side and the fixed throttle 13 inlet side and the use side heat exchanger 54 outlet side and the refrigerant suction port 15b are simultaneously performed. The two-electric four-way valve 52 is switched.

  Thereby, as shown by the solid line arrow in FIG. 25, the discharge port 10d of the compressor 10 (→ first electric four-way valve 51) → outdoor heat exchanger 53 (→ second electric four-way valve 52) → fixed throttle 13 The refrigerant circulates in the order of the liquid phase refrigerant outlet of the intermediate pressure side gas-liquid separator 14, the nozzle portion 15a, the gas phase refrigerant outlet of the accumulator 17, and the suction port 10b of the compressor 10, and the liquid phase refrigerant outlet of the accumulator 17 is variable. The refrigerant circulates in the order of the throttle mechanism 18 (→ first electric four-way valve 51) → use side heat exchanger 54 (→ second electric four-way valve 52) → refrigerant suction port 13b → accumulator 17, and intermediate pressure side gas-liquid separation. The gas phase refrigerant outlet of the vessel 14 and the intermediate pressure port 10 c of the compressor 10 are connected.

  Therefore, the first compression means 11a of the compressor 10 compresses and discharges the intermediate pressure refrigerant obtained by mixing the refrigerant discharged from the second compression means 21a and the gas phase refrigerant separated by the intermediate pressure side gas-liquid separator 14. Will do.

  Further, the refrigerant discharged from the first compression means 11a radiates heat in the outdoor heat exchanger 53, and the refrigerant radiated in the outdoor heat exchanger 53 flows into the fixed throttle 13 which is a high pressure side pressure reducing means. Further, the liquid phase refrigerant separated by the accumulator 17 flows into the use side heat exchanger 54, and the refrigerant flowing out from the use side heat exchanger 54 is sucked from the refrigerant suction port 15b.

  As a result, in the cooling operation mode of the present embodiment, the outdoor heat exchanger 53 corresponds to the radiator 12 in the first embodiment, and the use side heat exchanger 54 corresponds to the suction side evaporator 19 in the first embodiment. It becomes a structure, can operate | move similarly to 1st Embodiment, can cool the air in a store | warehouse | chamber, and can acquire the effect similar to 1st Embodiment.

  On the other hand, the heating operation mode is executed when the heating operation mode is selected by the operation switch of the operation panel. In the heating operation mode, the control device operates the first and second electric motors 11b and 21b and the blower fans 53a and 54a.

  Further, the control device simultaneously connects between the discharge port 10d side of the compressor 10 and the use side heat exchanger 54 inlet side, and between the variable throttle mechanism 18 outlet side and the outdoor heat exchanger 53 inlet side. The first electric four-way valve 51 is switched so that the outdoor heat exchanger 53 outlet side and the refrigerant suction port 15b and the use side heat exchanger 54 outlet side and the fixed throttle 13 inlet side are connected simultaneously. The two-electric four-way valve 52 is switched.

  As a result, as shown by the broken line arrow in FIG. 25, the discharge port 10d of the compressor 10 (→ first electric four-way valve 51) → use side heat exchanger 54 (→ second electric four-way valve 52) → fixed throttle The refrigerant circulates in the order of 13 → the liquid-phase refrigerant outlet of the intermediate pressure side gas-liquid separator 14 → the nozzle portion 15a → the gas-phase refrigerant outlet of the accumulator 17 → the suction port 10b of the compressor 10, and the liquid-phase refrigerant outlet of the accumulator 17 → The refrigerant circulates in the order of the variable throttle mechanism 18 (→ first electric four-way valve 51) → outdoor heat exchanger 53 (→ second electric four-way valve 52) → refrigerant suction port 13b → accumulator 17, and intermediate pressure side gas-liquid separation. The gas phase refrigerant outlet of the vessel 14 and the intermediate pressure port 10 c of the compressor 10 are connected.

  Therefore, the first compression means 11a of the compressor 10 compresses and discharges the intermediate pressure refrigerant obtained by mixing the refrigerant discharged from the second compression means 21a and the gas phase refrigerant separated by the intermediate pressure side gas-liquid separator 14. Will do.

  Further, the refrigerant discharged from the first compression means 11a radiates heat in the use side heat exchanger 54, and the refrigerant radiated in the use side heat exchanger 54 flows into the fixed throttle 13 which is a high pressure side pressure reducing means. Further, the liquid phase refrigerant separated by the accumulator 17 flows into the outdoor heat exchanger 53, and the refrigerant flowing out of the outdoor heat exchanger 53 is sucked from the refrigerant suction port 15b.

  Therefore, in the cooling operation mode of the present embodiment, the outdoor heat exchanger 53 corresponds to the suction side evaporator 19 in the first embodiment, and the use side heat exchanger 54 corresponds to the radiator 12 in the first embodiment. Thus, the internal air can be heated by operating in the same manner as in the first embodiment, and the same effect as in the first embodiment can be obtained.

  As a result, when the ejector refrigeration cycle 600 of the present embodiment is operated, both the compression efficiency improvement effect and the driving power reduction effect of the compression means are obtained in both the cooling operation mode and the heating operation mode. It can be sufficiently obtained to effectively improve the COP of the ejector refrigeration cycle.

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

  (1) In each of the above-described embodiments, the first and second compression units 11a and 21a are driven by different first and second electric motors 11b and 21b, respectively. The compression shafts of the means 11a and 21a may be shared, and both compression means may be driven by a driving force supplied from a common drive source.

  Further, in each of the above-described embodiments, the first and second compression means 11a and 21a are configured by different compression mechanisms, but an example has been described. However, the first and second compression means 11a and 21a are configured by the same compression mechanism. You can also

  For example, a scroll-type compression mechanism can be employed in which a communication port communicating with a compression chamber in a predetermined compression process is provided, and an intermediate pressure refrigerant is introduced through the communication port. In this case, a portion where the compression chamber is located on the downstream side (high pressure side) from the communication port is referred to as the first compression means 11a, and a portion located on the upstream side (low pressure side) from the communication port is referred to as the second compression means 21a. do it.

  (2) In the above-described embodiments, the first and second compression units 11a and 21a are driven by the first and second electric motors 11b and 21b. However, for example, an engine or the like may be used as a drive source. .

  Further, as the compression means, a variable capacity compression mechanism that can adjust the refrigerant discharge capacity by changing the discharge capacity may be adopted. In this case, the discharge capacity changing means becomes the discharge capacity changing means. Moreover, you may use the fixed capacity type compression mechanism which adjusts a refrigerant | coolant discharge capability by changing connection with a drive source intermittently by intermittent connection of an electromagnetic clutch. In this case, the electromagnetic clutch becomes the discharge capacity changing means.

  Furthermore, as the first and second compression units 11a and 21a, the same type of compression mechanism may be employed, or different types of compression mechanisms may be employed.

  (3) In the above-described embodiment, the fixed ejector 15 in which the throttle passage area of the nozzle portion 15a is fixed is adopted as the ejector 15. However, the variable ejector configured to be able to change the throttle passage area of the nozzle portion. May be adopted. Further, a variable throttle mechanism may be employed as the high pressure side pressure reducing means.

  Further, an intermediate pressure reducing means may be provided between the liquid phase refrigerant outlet of the intermediate pressure side gas-liquid separator 14 and the nozzle portion 15 a inlet side of the ejector 15. Thereby, the refrigerant in the gas-liquid two-phase state can be caused to flow into the nozzle portion 15a of the ejector 15, and the boiling of the refrigerant in the nozzle portion 15a is promoted in contrast to the case where the liquid-phase refrigerant is caused to flow into the nozzle portion 15a. Nozzle efficiency can be improved.

  Accordingly, the amount of boosted energy in the diffuser portion 15c can be increased by increasing the amount of recovered energy, so that the COP can be further improved. Furthermore, since the refrigerant passage area of the nozzle portion 15a can be expanded as compared with the case where the liquid phase refrigerant is caused to flow into the nozzle portion 15a, the processing of the nozzle portion 15a is facilitated. As a result, the manufacturing cost of the ejector 15 can be reduced, and the manufacturing cost of the entire ejector refrigeration cycle can be reduced.

  (4) 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 the 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-type refrigeration cycle 100 to 600 is a supercritical refrigeration cycle, the intermediate pressure side decompression means uses the high pressure side refrigerant pressure based on the high pressure side refrigerant temperature on the outlet side of the radiator 12. You may employ | adopt the pressure control valve adjusted to the target high pressure determined so that it may become substantially maximum.

  As such a pressure control valve, specifically, there is a temperature sensing part provided on the outlet side of the radiator 12, and a pressure corresponding to the temperature of the high-pressure refrigerant on the outlet side of the radiator 12 inside the temperature sensing part. The valve opening degree can be adjusted by a mechanical mechanism based on the balance between the internal pressure of the temperature sensing portion and the refrigerant pressure on the outlet side of the radiator 12.

  (5) In the above-described embodiment, the throttle mechanism is employed as the high pressure side pressure reducing means and the low pressure side pressure reducing means, but as the high pressure side pressure reducing means and the low pressure side pressure reducing means, the refrigerant is volume expanded to reduce the pressure, You may employ | adopt the expander which converts the pressure energy of a refrigerant | coolant into mechanical energy, and outputs it.

  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.

  (6) The means described in each embodiment described above can be applied to other embodiments. For example, an accumulator 17 similar to that of the first embodiment may be provided for the fifth and seventh to eleventh embodiments. Further, for example, the internal heat exchanger 30 similar to the second and third embodiments may be provided for the fifth, seventh to ninth, and eleventh embodiments.

  As the internal heat exchanger 30, a counter flow type heat exchanger in which the refrigerant flow direction in the high-pressure side refrigerant flow path and the refrigerant flow direction in the low-pressure side refrigerant flow path are different from each other may be adopted. A parallel flow heat exchanger in which the refrigerant flow direction in the refrigerant flow path and the refrigerant flow direction in the low-pressure side refrigerant flow path are the same may be employed.

  Further, in the ninth and eleventh embodiments, the outflow side evaporator 16 and the blower fan 16a may be eliminated and the internal heat exchanger 30 may be employed.

  For example, in the embodiment shown in FIG. 26, the outflow side evaporator 16 and the blower fan 16a are abolished with respect to the ninth embodiment, and the liquid phase refrigerant flowing out from the intermediate pressure side gas-liquid separator 14 and the diffuser portion 15c. This is an example in which an internal heat exchanger 30 for exchanging heat with the low-pressure refrigerant flowing out from the refrigerant, that is, the low-pressure refrigerant sucked into the second compression means 21a is employed.

  Further, as shown in FIG. 27, an internal heat exchanger 30 that exchanges heat between the high-pressure refrigerant flowing out of the auxiliary radiator 12e and the low-pressure refrigerant flowing out of the diffuser portion 15c may be employed. Thereby, the dryness of the refrigerant | coolant which flows into the intermediate pressure side gas-liquid separator 14 can be reduced, and the liquid phase refrigerant | coolant amount stored by the intermediate pressure side gas-liquid separator 14 can be increased. Therefore, even if load fluctuation occurs in the cycle, the refrigerant can be stably supplied to the suction side evaporator 19.

  Further, for example, in the embodiment shown in FIG. 28, compared with the eleventh embodiment, the outflow side evaporator 16 and the blower fan 16 a are abolished, and the liquid phase refrigerant that has flowed out from the intermediate pressure side gas-liquid separator 14 and the diffuser This is an example in which an internal heat exchanger 30 for exchanging heat with the low-pressure refrigerant flowing out from the section 15c, that is, the low-pressure refrigerant sucked into the second compression means 21a is employed.

  As shown in FIG. 29, an internal heat exchanger 30 that exchanges heat between the high-pressure refrigerant flowing out of the second radiator 122 and the low-pressure refrigerant flowing out of the diffuser portion 15c may be employed. Thereby, similarly to the cycle configuration shown in FIG. 27, the refrigerant can be stably supplied to the suction-side evaporator 19 even if a load fluctuation occurs in the cycle.

  Of course, a cycle configuration may be adopted in which the low-pressure side refrigerant flowing into the low-pressure side refrigerant flow path 30b of the internal heat exchanger 30 in FIGS. 26 to 29 is a refrigerant sucked into the refrigerant suction port 15b of the ejector 15.

  (7) In the above fifth to eleventh examples, the example in which the cooling target space (refrigerant space, freezer space) is cooled by the outflow side evaporator 16 and the suction side evaporator 19 has been described. The target space may be cooled. In this case, it is desirable that the outflow side evaporator 16 and the suction side evaporator 19 are assembled in an integrated structure, and the air blown from the blower fan is passed in the order of the outflow side evaporator 16 → the suction side evaporator 19.

  This is because the refrigerant evaporation pressure (refrigerant evaporation temperature) of the suction side evaporator 19 is lower than the refrigerant evaporation pressure (refrigerant evaporation temperature) of the outflow side evaporator 16. That is, by passing the blown air from the blower fan as described above, the temperature difference between the refrigerant evaporation temperature of the outflow side evaporator 16 and the suction side evaporator 19 and the blown air is secured, and the blown air is efficiently flowed. Can be cooled.

  (8) In the above-described eighth embodiment, the high-pressure branch operation mode is switched during high load operation, the low-pressure branch operation mode is switched during normal operation, and the simultaneous branch operation mode is switched during low-load operation. Of course, switching of each operation mode is not limited to this.

  For example, the high-pressure branch operation mode may be switched during high-load operation, the simultaneous branch operation mode during normal operation, and the low-pressure branch operation mode during low-load operation. That is, when the ejector refrigeration cycle 400 is operated, the operation mode may be switched to an operation mode in which the highest cycle efficiency can be exhibited.

  Moreover, it is good also as a cycle structure which switches a high voltage | pressure branch operation mode and a low voltage | pressure branch operation mode, without implement | achieving simultaneous branch operation mode. In this case, the first and second branch portions 22 and 28 may be configured by three-way valves to switch the refrigerant flow path.

  (9) In the twelfth embodiment, switching between the normal operation mode and the defrosting operation mode is performed based on the operation signal of the changeover switch on the operation panel, but switching between the normal operation mode and the defrosting operation mode is performed. It is not limited to this.

  For example, the control device may alternately switch between the normal operation mode and the defrosting operation mode every predetermined time. That is, when the normal operation mode is continued for a predetermined first reference time or longer, the mode is switched to the defrosting operation mode, and when the defrost operation mode is continued for a predetermined second reference time or longer, the normal operation is performed. You may make it switch to mode.

  Moreover, if the bypass passage 25 and the on-off valve 26 described above are applied to the fifth to eleventh embodiments in the same manner as the twelfth embodiment, the defrosting operation mode can be realized in the ejector refrigeration cycles 200 to 500. .

  (10) In the thirteenth embodiment, the example in which the first and second electric four-way valves 51 and 52 are employed as the refrigerant flow path switching unit has been described. However, the refrigerant flow path switching unit is not limited to this. For example, as shown in FIGS. 26 and 27, instead of the electric four-way valve 51, two electric three-way valves 51a may be combined, or four open / close valves (solenoid valves) 51b may be combined. May be.

  (11) In each of the above-described embodiments, examples in which the ejector refrigeration cycle 100 to 500 of the present invention is applied to a refrigerator, a freezing / refrigeration apparatus, and a cold storage container have been described. However, the application of the present invention is not limited thereto. . For example, the ejector refrigeration cycle may be applied to an air conditioner, another stationary refrigeration cycle apparatus, a vehicle air conditioner, and the like.

  (12) In each of the above-described first to twelfth embodiments, the outflow side evaporator 16 and the suction side evaporator 19 are configured as utilization side heat exchangers, and the radiator 12 is configured as an outdoor heat exchanger that radiates heat to the atmosphere side. However, as in the thirteenth embodiment, the outflow side evaporator 16 and the suction side heat exchanger 16 are configured as outdoor heat exchangers that absorb heat from a heat source such as the atmosphere, and the radiator 12 is made of air or water. It is good also as a heat pump cycle comprised as an indoor side heat exchanger which heats a to-be-heated refrigerant.

It is a whole block diagram of the ejector-type refrigerating cycle of 1st Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 1st Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 2nd Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 2nd Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 3rd Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 3rd Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 4th Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 4th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 5th Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 5th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 6th Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 6th Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 7th Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 7th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 8th Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 8th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 9th Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 9th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 10th Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 10th Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 11th Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 11th Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 12th Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 12th 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 in other embodiment. It is a whole block diagram which shows the modification of the ejector-type refrigerating cycle in other embodiment. It is a whole block diagram of another ejector type refrigerating cycle in other embodiments. It is a whole block diagram which shows the modification of another ejector-type refrigerating cycle in other embodiment. It is a block diagram of the flow-path switching means in other embodiment. It is a block diagram of another flow-path switching means in other embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of a prior art.

Explanation of symbols

11a, 21a 1st, 2nd compression means 11b, 21b 1st, 2nd electric motor 12, 121, 122 Radiator, 1st, 2nd radiator 12e Auxiliary radiator 13 Fixed throttle 14 Intermediate pressure side gas-liquid separator 15 Ejector 15a Nozzle portion 15b Refrigerant suction port 16 Outflow side evaporator 17 Accumulator 18, 28 First and second variable throttle mechanisms 19 Suction side evaporators 22, 32 First and second branch portions 25 Bypass passage 26 On-off valve 30, 31 Internal heat exchanger 51, 52 First and second electric four-way valve 53 Outdoor heat exchanger 54 User side heat exchanger

Claims (28)

First compression means (11a) for compressing and discharging the refrigerant;
A radiator (12) for radiating heat from the high-pressure refrigerant discharged from the first compression means (11a);
High-stage decompression means (13) for decompressing and expanding the high-pressure refrigerant flowing out of the radiator (12);
An intermediate pressure side gas-liquid separator (14) for separating the gas and liquid of the refrigerant decompressed and expanded by the high stage pressure reducing means (13);
The refrigerant is sucked from the refrigerant suction port (15b) by the flow of the high-speed jet refrigerant jetted from the nozzle part (15a) for decompressing and expanding the liquid-phase refrigerant separated by the intermediate pressure side gas-liquid separator (14). An ejector (15) for mixing and increasing the pressure of the jet refrigerant and the suction refrigerant sucked from the refrigerant suction port (15b);
A suction-side evaporator (19) that evaporates the refrigerant and flows it out to the refrigerant suction port (15b) side;
Second compression means (21a) for compressing and discharging the refrigerant flowing out of the ejector (15),
The first compression means (11a) compresses an intermediate pressure refrigerant obtained by mixing the refrigerant discharged from the second compression means (21a) and the gas phase refrigerant separated by the intermediate pressure side gas-liquid separator (14). And is designed to be discharged
A first discharge capacity changing means (11b) for changing the refrigerant discharge capacity of the first compression means (11a);
Second discharge capacity changing means (21b) for changing the refrigerant discharge capacity of the second compression means (21a);
Control means for controlling the first discharge capacity changing means (11b) and the second discharge capacity changing means (21b),
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 means (11a) and the second compression means (21a). Configured to be possible,
The control means includes the first discharge capacity changing means (11b) and the second pressure so that the pressure increase amount in the first compression mechanism (11a) is equal to the pressure increase amount in the second compression mechanism (21a). An ejector-type refrigeration cycle that controls the discharge capacity changing means (21b) . An outflow-side gas-liquid separator (17) for separating the gas-liquid of the refrigerant flowing out of the ejector (15);
And a suction-side decompression means (18) that decompresses and expands the liquid refrigerant separated by the outflow-side gas-liquid separator (17) and flows it out to the inlet side of the suction-side evaporator (19). The ejector type refrigeration cycle according to claim 1.   An outlet side evaporator (16) is provided between the outlet side of the ejector (15) and the suction side of the second compression means (21a) and evaporates the refrigerant flowing out of the ejector (15). The ejector-type refrigeration cycle according to claim 2. A branch part (32) for branching the flow of the refrigerant flowing out of the ejector (15);
Outflow side evaporation that is arranged between one outlet side of the branch part (32) and the suction side of the second compression means (21a) and evaporates one refrigerant branched by the branch part (32). A vessel (16),
A suction-side pressure reducing means (18) for decompressing and expanding the other refrigerant branched at the branching portion (32) to flow out to the inlet side of the suction-side evaporator (19). 2. The ejector refrigeration cycle according to 1.   The internal heat exchanger (30) for exchanging heat between the liquid-phase refrigerant separated by the intermediate-pressure side gas-liquid separator (14) and the low-pressure side refrigerant of the cycle is provided. The ejector type refrigeration cycle according to claim 1.   The ejector refrigeration cycle according to claim 5, wherein the low-pressure side refrigerant of the cycle is a refrigerant sucked into the refrigerant suction port (15b).   The ejector refrigeration cycle according to claim 5, wherein the low-pressure side refrigerant of the cycle is a refrigerant sucked into the second compression means (21a). A branch part (22) for branching the flow of the liquid-phase refrigerant separated by the intermediate pressure side gas-liquid separator (14);
Suction side decompression means (18) for decompressing and expanding the refrigerant flowing into the suction side evaporator (19),
The nozzle part (15a) decompresses and expands one of the refrigerants branched at the branch part (22),
2. The ejector refrigeration cycle according to claim 1, wherein the suction side decompression means (18) decompresses and expands the other refrigerant branched at the branch portion (22).   An outlet side evaporator (16) is provided between the outlet side of the ejector (15) and the suction side of the second compression means (21a) and evaporates the refrigerant flowing out of the ejector (15). The ejector-type refrigeration cycle according to claim 8.   The ejector according to claim 8 or 9, further comprising an internal heat exchanger (30) for exchanging heat between the other liquid-phase refrigerant branched at the branch portion (22) and the low-pressure side refrigerant of the cycle. Refrigeration cycle.   The ejector-type refrigeration according to claim 8 or 9, further comprising an internal heat exchanger (31) for exchanging heat between the refrigerant in the decompression and expansion process in the suction-side decompression means (18) and the low-pressure refrigerant in the cycle. cycle.   The ejector-type refrigeration cycle according to claim 10 or 11, wherein the low-pressure side refrigerant of the cycle is a refrigerant sucked into the refrigerant suction port (15b).   The ejector-type refrigeration cycle according to claim 10 or 11, wherein the low-pressure side refrigerant of the cycle is a refrigerant sucked into the second compression means (21a). A first branch portion (22) configured to be able to branch the flow of the liquid-phase refrigerant separated by the intermediate pressure side gas-liquid separator (14);
A second branch portion (32) configured to be able to branch the flow of the refrigerant flowing out of the ejector (15);
One refrigerant disposed between one outlet side of the second branch portion (32) and the suction side of the second compression means (21a) evaporates one refrigerant branched at the second branch portion (32). An outflow evaporator (16) for
First and second suction side decompression means (18, 28) for decompressing and expanding the refrigerant flowing into the suction side evaporator (19),
The nozzle part (15a) decompresses and expands one of the refrigerants branched at the first branch part (22),
The first suction side decompression means (18) decompresses and expands the other refrigerant branched at the first branch part (22),
The second suction side decompression means (28) decompresses and expands the other refrigerant branched at the second branch portion (32),
The said suction side evaporator (19) evaporates at least one among the refrigerant | coolants expanded and decompressed by the said 1st, 2nd suction side decompression means (18, 28), The feature of Claim 1 characterized by the above-mentioned. Ejector type refrigeration cycle.   The ejector according to claim 14, further comprising an internal heat exchanger (30) for exchanging heat between the other liquid-phase refrigerant branched at the first branch portion (22) and the low-pressure side refrigerant of the cycle. Refrigeration cycle.   The ejector-type refrigeration cycle according to claim 15, wherein the low-pressure side refrigerant of the cycle is a refrigerant sucked into the refrigerant suction port (15b).   The ejector refrigeration cycle according to claim 15, wherein the low-pressure side refrigerant of the cycle is a refrigerant sucked into the second compression means (21a). First compression means (11a) for compressing and discharging the refrigerant;
A radiator (12) for radiating heat from the high-pressure refrigerant discharged from the first compression means (11a);
A branch part (22) for branching the flow of the refrigerant flowing out of the radiator (12);
The refrigerant is sucked from the refrigerant suction port (15b) by the flow of the high-speed jet refrigerant jetted from the nozzle part (15a) for decompressing and expanding one of the refrigerants branched at the branch part (22), and the jetted refrigerant And an ejector (15) for mixing and increasing the suction refrigerant sucked from the refrigerant suction port (15b),
An auxiliary radiator (12e) for radiating heat from the other refrigerant branched at the branch portion (22);
High-stage decompression means (13) for decompressing and expanding the refrigerant flowing out of the auxiliary radiator (12e);
An intermediate pressure side gas-liquid separator (14) for separating the gas and liquid of the refrigerant decompressed and expanded by the high stage pressure reducing means (13);
Suction side decompression means (18) for decompressing and expanding the liquid refrigerant separated by the intermediate pressure side gas-liquid separator (14);
A suction-side evaporator (19) for evaporating the refrigerant decompressed and expanded by the suction-side decompression means (18) and causing the refrigerant to flow out to the refrigerant suction port (15b) side;
Second compression means (21a) for compressing and discharging the refrigerant flowing out of the ejector (15),
The first compression means (11a) compresses an intermediate pressure refrigerant obtained by mixing the refrigerant discharged from the second compression means (21a) and the gas phase refrigerant separated by the intermediate pressure side gas-liquid separator (14). And is designed to be discharged
A first discharge capacity changing means (11b) for changing the refrigerant discharge capacity of the first compression means (11a);
Second discharge capacity changing means (21b) for changing the refrigerant discharge capacity of the second compression means (21a);
Control means for controlling the first discharge capacity changing means (11b) and the second discharge capacity changing means (21b),
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 means (11a) and the second compression means (21a). Configured to be possible,
The control means includes the first discharge capacity changing means (11b) and the second pressure so that the pressure increase amount in the first compression mechanism (11a) is equal to the pressure increase amount in the second compression mechanism (21a). An ejector-type refrigeration cycle that controls the discharge capacity changing means (21b) . First compression means (11a) for compressing and discharging the refrigerant;
A branch part (22) for branching the flow of the high-pressure refrigerant discharged from the first compression means (11a);
A first radiator (121) for radiating heat from one of the refrigerants branched at the branch part (22);
The refrigerant is sucked from the refrigerant suction port (15b) by the flow of the high-speed jet refrigerant jetted from the nozzle portion (15a) for decompressing and expanding the refrigerant flowing out from the first radiator (121), and the jet refrigerant and the An ejector (15) for mixing and boosting the suction refrigerant sucked from the refrigerant suction port (15b);
A second radiator (122) for radiating heat from the other refrigerant branched at the branch portion (22);
High-stage decompression means (13) for decompressing and expanding the high-pressure refrigerant flowing out of the second radiator (122);
An intermediate pressure side gas-liquid separator (14) for separating the gas and liquid of the refrigerant decompressed and expanded by the high stage pressure reducing means (13);
Suction-side decompression means (18) for decompressing and expanding the liquid refrigerant separated by the intermediate pressure-side gas-liquid separator (14);
A suction-side evaporator (19) for evaporating the refrigerant flowing out from the suction-side decompression means (18) and causing the refrigerant to flow out toward the refrigerant suction port (15b);
Second compression means (21a) for compressing and discharging the refrigerant flowing out of the ejector (15),
The first compression means (11a) compresses an intermediate pressure refrigerant obtained by mixing the refrigerant discharged from the second compression means (21a) and the gas phase refrigerant separated by the intermediate pressure side gas-liquid separator (14). And is designed to be discharged
A first discharge capacity changing means (11b) for changing the refrigerant discharge capacity of the first compression means (11a);
Second discharge capacity changing means (21b) for changing the refrigerant discharge capacity of the second compression means (21a);
Control means for controlling the first discharge capacity changing means (11b) and the second discharge capacity changing means (21b),
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 means (11a) and the second compression means (21a). Configured to be possible,
The control means includes the first discharge capacity changing means (11b) and the second pressure so that the pressure increase amount in the first compression mechanism (11a) is equal to the pressure increase amount in the second compression mechanism (21a). An ejector-type refrigeration cycle that controls the discharge capacity changing means (21b) .   An outlet side evaporator (16) is provided between the outlet side of the ejector (15) and the suction side of the second compression means (21a) and evaporates the refrigerant flowing out of the ejector (15). The ejector type refrigeration cycle according to claim 18 or 19.   21. An internal heat exchanger (30) for exchanging heat between the liquid refrigerant flowing out of the intermediate pressure side gas-liquid separator (14) and the low pressure side refrigerant of the cycle is provided. Ejector type refrigeration cycle described in 1.   The ejector-type refrigeration cycle according to claim 21, wherein the low-pressure side refrigerant of the cycle is a refrigerant sucked into the refrigerant suction port (15b).   The ejector refrigeration cycle according to claim 21, wherein the low-pressure side refrigerant of the cycle is a refrigerant sucked into the second compression means (21a). A bypass passage (25) for guiding the high-pressure side refrigerant of the cycle discharged from the first compression means (11a) to the suction-side evaporator (19);
The ejector refrigeration cycle according to any one of claims 1 to 23, further comprising an opening / closing means (26) for opening and closing the bypass passage (25). First compression means (11a) for compressing and discharging the refrigerant;
A use side heat exchanger (54) for exchanging heat between the refrigerant and the fluid to be heat exchanged;
An outdoor heat exchanger (53) for exchanging heat between the refrigerant and the outside air;
A refrigerant channel switching means (51, 52) for switching between 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;
High-pressure side decompression means for decompressing and expanding the refrigerant radiated in the outdoor heat exchanger (53) or the use side heat exchanger (54) during at least one of the cooling operation mode and the heating operation mode. 13)
An intermediate pressure side gas-liquid separator (14) for separating the gas-liquid of the refrigerant decompressed and expanded by the high-pressure side pressure reducing means (13)
The refrigerant is sucked from the refrigerant suction port (15b) by the flow of the high-speed jet refrigerant jetted from the nozzle part (15a) for decompressing and expanding the liquid-phase refrigerant separated by the intermediate pressure side gas-liquid separator (14). An ejector (15) for mixing and increasing the pressure of the jet refrigerant and the suction refrigerant sucked from the refrigerant suction port (15b);
Second compression means (21a) for compressing and discharging the refrigerant flowing out of the ejector (15),
The first compression means (11a) compresses an intermediate pressure refrigerant obtained by mixing the refrigerant discharged from the second compression means (21a) and the gas phase refrigerant separated by the intermediate pressure side gas-liquid separator (14). And then discharge
The refrigerant flow switching means (51, 52)
In the cooling operation mode, the refrigerant discharged from the first compression means (11a) is radiated by the outdoor heat exchanger (53), and the refrigerant flowing out of the use side heat exchanger (54) is discharged to the refrigerant. Switch to the refrigerant flow path leading to the suction port (15b) side,
In the heating operation mode, the refrigerant discharged from the first compression means (11a) is radiated by the use side heat exchanger (54), and the refrigerant flowing out of the outdoor heat exchanger (53) is discharged to the refrigerant. Switching to the refrigerant flow path leading to the suction port (15b) side ,
A first discharge capacity changing means (11b) for changing the refrigerant discharge capacity of the first compression means (11a);
Second discharge capacity changing means (21b) for changing the refrigerant discharge capacity of the second compression means (21a);
Control means for controlling the first discharge capacity changing means (11b) and the second discharge capacity changing means (21b),
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 means (11a) and the second compression means (21a). Configured to be possible,
The control means includes the first discharge capacity changing means (11b) and the second pressure so that the pressure increase amount in the first compression mechanism (11a) is equal to the pressure increase amount in the second compression mechanism (21a). An ejector-type refrigeration cycle that controls the discharge capacity changing means (21b) . Furthermore, an outflow side gas-liquid separator (17) for separating the gas-liquid of the refrigerant that has flowed out of the ejector (15) is provided,
The gas-phase refrigerant outlet of the outflow side gas-liquid separator (17) is connected to the suction port side of the second compression means (21a),
The refrigerant flow switching means (51, 52)
In the cooling operation mode, the refrigerant radiated by the outdoor heat exchanger (53) is caused to flow into the high-pressure side decompression means (13), and the liquid-phase refrigerant separated by the outflow-side gas-liquid separator (17). Is switched to a refrigerant flow path for flowing into the use side heat exchanger (54),
In the heating operation mode, the refrigerant radiated by the use side heat exchanger (54) is caused to flow into the high pressure side pressure reducing means (13), and the liquid phase separated by the outflow side gas-liquid separator (17). 26. The ejector refrigeration cycle according to claim 25, wherein the refrigerant flow is switched to a refrigerant flow path for allowing the refrigerant to flow into the outdoor heat exchanger (53). The first compressing means (11a) and said second compressing means (21a) is accommodated in the same housing, any one of claims 1 to 26, characterized in that it is integrally formed The ejector-type refrigeration cycle described in 1. The ejector refrigeration cycle according to any one of claims 1 to 27 , wherein the first compression means (11a) increases the pressure of the refrigerant until the pressure becomes equal to or higher than a critical pressure.

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