JP5206362B2 - Ejector refrigeration cycle - Google Patents

Description

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

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

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

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

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

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

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

The recovered kinetic energy (hereinafter referred to as “recovered energy”) is converted into pressure energy by the diffuser portion of the ejector to increase the pressure of the compressor suction refrigerant, thereby reducing the driving power of the compressor. The coefficient of performance (COP) of the ejector refrigeration cycle is improved.
Japanese Patent No. 3322263 Japanese Patent No. 3931899 JP 2008-107055 A

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

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

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

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

  This will be described in detail with reference to FIG. FIG. 76 is a Mollier diagram showing the state of the refrigerant in the ejector refrigeration cycle of Patent Document 1 (see FIG. 2 of Patent Document 1). Note that the solid line in FIG. 76 shows the state of the refrigerant during normal operation, and the broken line shows the state of the refrigerant when the above-described cycle failure occurs.

As is apparent from FIG. 76, when the pressure difference between the high-pressure refrigerant and the low-pressure refrigerant is reduced due to a decrease in the outside air temperature or the like (open arrow X _{76 in} FIG. ₇₆ ), the suction capacity of the ejector is lowered. As a result, when the refrigerant is not supplied to the evaporator, the low-pressure refrigerant cannot exhibit the endothermic action in the evaporator (the white arrow Y _{76 in} FIG. ₇₆ ).

  For this reason, as shown by the broken line in FIG. 76, the amount of heat that the refrigerant can radiate with the radiator becomes equivalent to the compression work of the compressor. As a result, the amount of heat cannot be substantially transferred from the low pressure side to the high pressure side via the refrigerant, and the cycle fails.

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

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

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

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

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

  That is, in the ejector type refrigeration cycle using the ejector as the refrigerant pressure reducing means, there is a problem that when the flow rate fluctuation of the driving flow occurs, the cycle cannot be stably operated while exhibiting a high COP.

  In addition, this problem becomes significant in an ejector refrigeration cycle in which the difference between high and low pressures of the cycle during normal operation is large. The reason is that, generally, in an ejector-type refrigeration cycle with a large difference between high and low pressures, the refrigerant evaporation pressure in the suction-side evaporator is low, and therefore the proportion of the pressure increase in the diffuser portion of the refrigerant pressure increase is large. is there.

  Furthermore, in an ejector type refrigeration cycle having a large difference between high and low pressures, the refrigerant evaporation temperature in the suction side evaporator is also low, so there is a concern that the suction side evaporator may form frost. When such frost formation occurs, it becomes difficult for the endothermic fluid (for example, the atmosphere) to flow through the suction-side evaporator, and the heat absorption of the refrigerant is hindered. As a result, even in the ejector refrigeration cycle of Patent Documents 2 and 3, the failure of the cycle occurs.

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

Moreover, in invention of Claim 1 , the 1st compression mechanism (11a) which compresses and discharges a refrigerant | coolant, The heat radiator (12) which radiates the high pressure refrigerant | coolant discharged from the 1st compression mechanism (11a), High-speed injection that injects from the branch part (18) that branches the flow of the refrigerant flowing out from the radiator (12) and the nozzle part (13a) that decompresses and expands one of the refrigerants branched by the branch part (18) An ejector (13) that sucks the refrigerant from the refrigerant suction port (13b) by the flow of the refrigerant and boosts the mixed refrigerant of the injected refrigerant and the suction refrigerant sucked from the refrigerant suction port (13b) at the diffuser portion (13d). And a suction side decompression means (19) for decompressing and expanding the other refrigerant branched at the branch section (18), and a refrigerant decompressed and expanded by the suction side decompression means (19) to evaporate, (13b) Let it flow to the side A suction side evaporator (16), a second compression mechanism (21a) for sucking and compressing the suction side evaporator (16) outlet side refrigerant and discharging it to the refrigerant suction port (13b) side, and a high pressure side refrigerant of the cycle It is characterized by an ejector refrigeration cycle comprising a bypass passage (25) for guiding the gas to the suction side evaporator (16) and an opening / closing means (26) for opening and closing the bypass passage (25).

  According to this, during normal operation in which the opening / closing means (26) closes the bypass passage (25), the operating conditions are such that the suction capacity of the ejector (13) decreases as the drive flow rate of the ejector (13) decreases. Even in this case, the ejector refrigeration cycle can be stably operated in a state in which a high COP is exhibited, as in the invention described in claim 1.

  That is, by increasing the suction pressure of the first compression mechanism (11a) by the pressure increasing action of the diffuser part (13d), not only the compressor driving power of the first compression mechanism (11a) is reduced, but also the respective first Since the pressure difference between the suction pressure and the discharge pressure of the first and second compression mechanisms (11a, 21a) can be reduced, the compression efficiency of the first and second compression mechanisms (11a, 21a) can be improved.

  As a result, even if the flow rate fluctuation of the driving flow occurs and the boosting capability of the diffuser section (13d) decreases, the ejector refrigeration cycle can be stably operated in a state where a high COP is exhibited.

  In addition, when frosting occurs in the suction side evaporator (16), the opening / closing means (26) is opened, so that the high-temperature refrigerant discharged from the first compression mechanism (11a) is directly taken into the suction side evaporator (16). ) To be defrosted and defrosted. Therefore, it is possible to avoid the cycle failure due to the frost formation of the suction side evaporator (16), and to stably operate the ejector refrigeration cycle.

The invention according to claim 2 is characterized in that the ejector refrigeration cycle according to claim 1 is provided with an outflow side evaporator (14) for evaporating the refrigerant flowing out from the diffuser section (13d). According to this, during the normal operation in which the opening / closing means (26) closes the bypass passage (25), not only the suction side evaporator (16) but also the outflow side evaporator (14) can exhibit the refrigerating capacity.

  Further, in the suction side evaporator (16), the refrigerant evaporating pressure corresponds to the suction action of the injected refrigerant, and in the outflow side evaporator (14), the refrigerant evaporating pressure after being boosted by the diffuser portion (13d). Therefore, the refrigerant | coolant evaporation temperature of a suction side evaporator (16) and an outflow side evaporator (14) can be made into a different temperature.

According to a third aspect of the present invention, in the ejector-type refrigeration cycle according to the second aspect , the high-pressure refrigerant discharged from the first compression mechanism (11a) bypasses the radiator (12), and the outflow side evaporator And an auxiliary bypass passage (25a) leading to (14). According to this, the high-temperature refrigerant | coolant discharged from the 1st compression mechanism (11a) can be guide | induced to an outflow side evaporator (14), and can be defrosted.

Further, as in the invention according to claim 4 , in the ejector refrigeration cycle according to any one of claims 1 to 3 , the high-pressure side refrigerant of the cycle is a refrigerant on the upstream side of the radiator (12). The bypass passage (25) may bypass the heat radiator (12) to guide the refrigerant on the upstream side of the heat radiator (12) to the suction side evaporator (16).

Further, as in the invention described in claim 5 , the heat dissipation capability adjusting means (12a) for adjusting the heat dissipation capability of the radiator (12) is provided, and the high-pressure side refrigerant of the cycle is a refrigerant on the downstream side of the radiator (12). And the heat dissipation capability adjusting means (12a) may reduce the heat dissipation capability of the radiator (12) when the opening / closing means (26) opens the bypass passage (25).

  Thus, during the defrosting operation in which the opening / closing means (26) opens the bypass passage (25), the high-temperature refrigerant discharged from the first compression mechanism (11a) is reliably supplied to the suction-side evaporator (16) for suction. The side evaporator (16) can be defrosted.

The invention according to claim 6, in refrigerant cycle according to any one of claims 1 to 5, arranged in the refrigerant passage leading from the radiator (12) outlet to the nozzle portion (13a) inlet side And a high-pressure side decompression means (17) for decompressing and expanding the refrigerant flowing out of the radiator (12).

  According to this, during the normal operation in which the opening / closing means (26) closes the bypass passage (25), the refrigerant flowing into the nozzle part (13a) becomes a gas-liquid two-phase refrigerant by the action of the high pressure side pressure reducing means (17). Can be depressurized. Therefore, compared with the case where the liquid refrigerant is introduced into the nozzle part (13a), the boiling of the refrigerant in the nozzle part (13a) can be promoted to improve the nozzle efficiency.

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

  Further, by configuring the high-pressure side pressure reducing means (17) with a variable throttle mechanism, it is possible to change the flow rate of the refrigerant flowing into the nozzle portion (13a) according to the cycle load fluctuation. As a result, even when load fluctuation occurs, the cycle can be stably operated while exhibiting a high COP.

Specifically, the high pressure side pressure reducing means (17) may be arranged in the refrigerant passage from the radiator (12) outlet side to the branching portion (18) inlet side, as in the seventh aspect of the invention.

In the invention described in claim 8, in refrigerant cycle according to any one of claims 1 to 7, when opening and closing means (26) which closes the bypass passage (25), the radiator (12) And an internal heat exchanger (30) for exchanging heat between the refrigerant flowing out of the refrigerant and the low-pressure side refrigerant of the cycle.

  According to this, the enthalpy difference (refrigeration capacity) between the enthalpy of the inlet side refrigerant and the enthalpy of the outlet side refrigerant can be increased and the COP can be improved.

Specifically, the refrigerant that has flowed out of the radiator (12) flows through the refrigerant passage from the branch portion (18) outlet side to the suction side pressure reducing means (19) inlet side, as in the ninth aspect of the invention. A refrigerant may be used.

In the invention according to claim 10, in the ejector type refrigeration cycle according to any one of claims 1 to 7, when opening and closing means (26) which closes the bypass passage (25), the suction side pressure reducing means ( The internal heat exchanger (31) for exchanging heat between the refrigerant in the decompression and expansion process in 19) and the low-pressure side refrigerant of the cycle is provided.

  According to this, the enthalpy difference (refrigeration capacity) between the enthalpy of the inlet side refrigerant and the enthalpy of the outlet side refrigerant can be increased and the COP can be improved.

Specifically, the low-pressure side refrigerant of the cycle may be a refrigerant sucked into the first compression mechanism (11a) as in the invention described in claim 11 , or as in the invention described in claim 12. Alternatively, the refrigerant may be sucked into the second compression mechanism (21a).

The invention according to claim 13, in the ejector type refrigeration cycle according to any one of claims 1 to 12, disposed in a refrigerant flow downstream side of the branch portion (18), closing means (26) is bypassed When the passage (25) is closed, an auxiliary radiator (12e) that radiates the refrigerant flowing into the suction-side decompression means (19) is provided.

  According to this, since the low enthalpy refrigerant cooled by both the radiator (12) and the auxiliary radiator (12e) can flow into the suction side evaporator (16), the suction side evaporator (16). COP can be improved by expanding the enthalpy difference (refrigeration capacity) between the enthalpy of the inlet side refrigerant and the enthalpy of the outlet side refrigerant.

  At this time, since the refrigerant flowing into the nozzle part (13a) of the ejector (13) 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 (19). Thereby, the recovery energy amount in the nozzle part 13a can be increased, and COP can be further improved.

The invention according to claim 14, in the ejector type refrigeration cycle according to any one of claims 1 to 13, disposed between the suction side evaporator (16) and the second compression mechanism (21a) A suction-side gas-liquid separator (22) for separating the gas-liquid refrigerant, and the gas-phase refrigerant outlet of the suction-side gas-liquid separator (22) is connected to the suction port side of the second compression mechanism (21a). It is characterized by being.

  According to this, even if the liquid refrigerant flows out from the suction side evaporator (16) or the high-temperature refrigerant condenses during the defrosting operation of the suction side evaporator (16), the suction side gas-liquid separator Since only the gas-phase refrigerant separated in (22) can be supplied to the second compression mechanism (21a), the problem of liquid compression of the second compression mechanism (21a) can be avoided.

In the invention according to claim 15 , the first compression mechanism (11a) that compresses and discharges the refrigerant, the radiator (12) that radiates heat from the high-pressure refrigerant discharged from the first compression mechanism (11a), The refrigerant is sucked from the refrigerant suction port (13b) by the flow of the high-speed jet refrigerant jetted from the nozzle (13a) that decompresses and expands the refrigerant flowing out of the radiator (12), and the jetted refrigerant and the refrigerant suction port (13b) The ejector (13) for boosting the mixed refrigerant with the suction refrigerant sucked from the diffuser part (13d), the branch part (18) for branching the flow of the refrigerant flowing out from the diffuser part (13d), and the branch part An outlet side evaporator (14) that evaporates one refrigerant branched in (18) and flows out to the suction side of the first compression mechanism (11a), and the other refrigerant branched in the branch portion (18). The decompression expanded Suction side pressure reducing means (19), a suction side evaporator (16) for evaporating the refrigerant decompressed and expanded by the suction side pressure reducing means (19) and flowing it out to the refrigerant suction port (13b) side, and a suction side A second compression mechanism (21a) that sucks and compresses the outlet side refrigerant of the evaporator (16) and discharges it to the refrigerant suction port (13b) side, and guides the high-pressure side refrigerant of the cycle to the suction side evaporator (16). An ejector refrigeration cycle including a bypass passage (25) and an opening / closing means (26) for opening and closing the bypass passage (25) is characterized.

  According to this, during normal operation in which the opening / closing means (26) closes the bypass passage (25), the operating conditions are such that the suction capacity of the ejector (13) decreases as the drive flow rate of the ejector (13) decreases. Even in this case, the ejector refrigeration cycle can be stably operated in a state in which a high COP is exhibited, as in the invention described in claim 1.

  That is, by increasing the suction pressure of the first compression mechanism (11a) by the pressure increasing action of the diffuser part (13d), not only the compressor driving power of the first compression mechanism (11a) is reduced, but also the respective first Since the pressure difference between the suction pressure and the discharge pressure of the first and second compression mechanisms (11a, 21a) can be reduced, the compression efficiency of the first and second compression mechanisms (11a, 21a) can be improved.

  As a result, even if the flow rate fluctuation of the driving flow occurs and the boosting capability of the diffuser section (13d) decreases, the ejector refrigeration cycle can be stably operated in a state where a high COP is exhibited.

  Further, in the outflow side evaporator (14), the refrigerant evaporation pressure (refrigerant evaporation temperature) is increased after being increased in pressure in the diffuser part (13d), and in the suction side evaporator (16), the pressure is increased in the diffuser part (13d). Then, the refrigerant evaporating pressure after the refrigerant is further depressurized by the suction side depressurizing means (19) is set to a different evaporating temperature between the suction side evaporator (16) and the outflow side evaporator (14). can do.

  In addition, when frosting occurs in the suction side evaporator (16), the opening / closing means (26) is opened, so that the high-temperature refrigerant discharged from the first compression mechanism (11a) is directly taken into the suction side evaporator (16). ) To be defrosted and defrosted. Therefore, it is possible to avoid the cycle failure due to the frost formation of the suction side evaporator (16), and to stably operate the ejector refrigeration cycle.

In the ejector-type refrigeration cycle according to claim 15 , as in the invention according to claim 16 , the suction side pressure reducing means (19) restricts the throttle when the opening / closing means (26) closes the bypass passage (25). It may be configured by a variable throttle mechanism that decreases the opening degree, or may be configured by a variable throttle mechanism that increases the throttle opening degree, as in the invention described in claim 17 .

  It should be noted that “reducing the throttle opening” in this claim includes not only the meaning of reducing the refrigerant passage area but also the meaning of fully closing the throttle opening. Furthermore, “increasing the throttle opening” includes not only the meaning of expanding the refrigerant passage area but also the meaning of fully opening the throttle opening.

Further, as in the invention described in claim 18 , in the ejector refrigeration cycle according to any one of claims 15 to 17 , the high-pressure side refrigerant of the cycle is a refrigerant on the upstream side of the radiator (12). The bypass passage (25) may bypass the heat radiator (12) to guide the refrigerant on the upstream side of the heat radiator (12) to the suction side evaporator (16).

Further, as in the invention described in claim 19 , the heat dissipation capability adjusting means (12 a) for adjusting the heat dissipation capability of the radiator (12) is provided, and the high-pressure side refrigerant of the cycle is a refrigerant on the downstream side of the radiator (12). And the heat dissipation capability adjusting means (12a) may reduce the heat dissipation capability of the radiator (12) when the opening / closing means (26) opens the bypass passage (25).

  Thus, during the defrosting operation in which the opening / closing means (26) opens the bypass passage (25), the high-temperature refrigerant discharged from the first compression mechanism (11a) is reliably supplied to the suction-side evaporator (16) for suction. The side evaporator (16) can be defrosted.

According to a nineteenth aspect of the present invention, in the ejector refrigeration cycle according to any one of the fifteenth to nineteenth aspects, the refrigerant refrigeration cycle is disposed in a refrigerant passage extending from the radiator (12) outlet side to the nozzle portion (13a) inlet side. And a high-pressure side decompression means (17) for decompressing and expanding the refrigerant flowing out of the radiator (12).

  According to this, during the normal operation in which the opening / closing means (26) closes the bypass passage (25), the refrigerant flowing into the nozzle part (13a) becomes a gas-liquid two-phase refrigerant by the action of the high pressure side pressure reducing means (17). Can be depressurized. Therefore, compared with the case where the liquid refrigerant is introduced into the nozzle part (13a), the boiling of the refrigerant in the nozzle part (13a) can be promoted to improve the nozzle efficiency.

  As a result, the amount of pressure increase in the diffuser section (13d) can be increased to further improve the COP. Further, by configuring the high-pressure side pressure reducing means (17) with a variable throttle mechanism, it is possible to change the flow rate of the refrigerant flowing into the nozzle portion (13a) according to the cycle load fluctuation. Furthermore, even if load fluctuation occurs, the cycle can be stably operated while exhibiting high COP.

The invention according to claim 21, in the ejector type refrigeration cycle as claimed in any one of claims 15 to 20, is disposed between the suction side evaporator (16) and the second compression mechanism (21a) A suction-side gas-liquid separator (22) for separating the gas-liquid refrigerant, and the gas-phase refrigerant outlet of the suction-side gas-liquid separator (22) is connected to the suction port side of the second compression mechanism (21a). It is characterized by being.

  According to this, even if the liquid refrigerant flows out from the suction side evaporator (16) or the high-temperature refrigerant condenses during the defrosting operation of the suction side evaporator (16), the suction side gas-liquid separator Since only the gas-phase refrigerant separated in (22) can be supplied to the second compression mechanism (21a), the problem of liquid compression of the second compression mechanism (21a) can be avoided.

In the invention according to claim 22 , a first compression mechanism (11a) that compresses and discharges the refrigerant, a radiator (12) that radiates heat from the high-pressure refrigerant discharged from the first compression mechanism (11a), The refrigerant is sucked from the refrigerant suction port (13b) by the flow of the high-speed jet refrigerant jetted from the nozzle (13a) that decompresses and expands the refrigerant flowing out of the radiator (12), and the jetted refrigerant and the refrigerant suction port (13b) ) Evaporating the refrigerant flowing out of the ejector (13) and the ejector (13) that boosts the mixed refrigerant with the suction refrigerant sucked from the diffuser section (13d), and suctioning the first compression mechanism (11a) The flow is branched at the outflow side evaporator (14) that flows out into the air, the first branch section (18) configured to be able to branch the refrigerant flow out of the radiator (12), and the first branch section (18). Decompressed refrigerant The first suction side pressure reducing means (19) to be branched, the second branch portion (28) configured to be able to branch the flow of the refrigerant flowing out from the diffuser portion (13), and the second branch portion (28) are branched. At least one of the second suction side decompression means (29) for decompressing and expanding the refrigerant, the refrigerant flowing out from the first suction side decompression means (19), and the refrigerant flowing out from the second suction side decompression means (29) The suction side evaporator (16) that evaporates one refrigerant and flows out to the refrigerant suction port (13b) side, and the suction side evaporator (16) outlet side refrigerant is sucked and compressed, and the refrigerant suction port (13b) A second compression mechanism (21a) that discharges to the side, a bypass passage (25) that guides the high-pressure refrigerant of the cycle to the suction-side evaporator (16), and an opening and closing means (26) that opens and closes the bypass passage (25) Ejector refrigeration cycle equipped with To.

  According to this, during the normal operation in which the opening / closing means (26) closes the bypass passage (25), the refrigerant flow is branched only by the first branch portion (18), and the first suction side pressure reducing means (19) By supplying the flowing refrigerant to the suction side evaporator (16), a cycle configuration corresponding to the cycle configuration of Patent Document 2 can be realized.

  Further, the flow of the refrigerant is branched only by the second branch part (28), and only the refrigerant that has flowed out from the second suction side pressure reducing means (29) is supplied to the suction side evaporator (16). A cycle configuration corresponding to the three cycle configurations can be realized. Further, the refrigerant flow is branched at both the first and second branch parts (18, 28), and the refrigerant flowing out from both the first and second suction side decompression means (19, 29) is sucked into the suction side evaporator. The cycle configuration supplied to (16) can be realized.

  This makes it easier to increase the flow rate of the refrigerant supplied to the suction-side evaporator (16) with respect to the cycle configuration in which the refrigerant is supplied from one of the suction-side decompression means (19, 29) during normal operation.

  Furthermore, even if it switches to any cycle structure at the time of a normal driving | operation, it is at the time of the driving | running condition that the attraction | suction capability of an ejector (13) falls with the flow volume fall of the drive flow of an ejector (13). Similarly to the invention, the ejector refrigeration cycle can be stably operated in a state where a high COP is exhibited.

  That is, by increasing the suction pressure of the first compression mechanism (11a) by the pressure increasing action of the diffuser part (13d), not only the compressor driving power of the first compression mechanism (11a) is reduced, but also the respective first Since the pressure difference between the suction pressure and the discharge pressure of the first and second compression mechanisms (11a, 21a) can be reduced, the compression efficiency of the first and second compression mechanisms (11a, 21a) can be improved.

  As a result, even if the flow rate fluctuation of the driving flow occurs and the boosting capability of the diffuser section (13d) decreases, the ejector refrigeration cycle can be stably operated in a state where a high COP is exhibited.

  In addition, when frosting occurs in the suction side evaporator (16), the opening / closing means (26) is opened, so that the high-temperature refrigerant discharged from the first compression mechanism (11a) is directly taken into the suction side evaporator (16). ) To be defrosted and defrosted. Therefore, it is possible to avoid the cycle failure due to the frost formation of the suction side evaporator (16), and to stably operate the ejector refrigeration cycle.

In the ejector-type refrigeration cycle according to claim 22 , as in the invention according to claim 23 , the second suction side pressure reducing means (29) is provided when the opening / closing means (26) closes the bypass passage (25). Further, it may be constituted by a variable throttle mechanism for reducing the throttle opening degree, or may be constituted by a variable throttle mechanism for increasing the throttle opening degree as in the invention described in claim 24 .

  It should be noted that “reducing the throttle opening” in this claim includes not only the meaning of reducing the refrigerant passage area but also the meaning of fully closing the throttle opening. Furthermore, “increasing the throttle opening” includes not only the meaning of expanding the refrigerant passage area but also the meaning of fully opening the throttle opening.

Further, as in the invention described in claim 27 , in the ejector refrigeration cycle according to any one of claims 22 to 24 , the high-pressure side refrigerant of the cycle is a refrigerant on the upstream side of the radiator (12). The bypass passage (25) may bypass the heat radiator (12) to guide the refrigerant on the upstream side of the heat radiator (12) to the suction side evaporator (16).

Further, as in the invention described in claim 26 , the heat dissipation capability adjusting means (12a) for adjusting the heat dissipation capability of the radiator (12) is provided, and the high-pressure side refrigerant of the cycle is a refrigerant on the downstream side of the radiator (12). And the heat dissipation capability adjusting means (12a) may reduce the heat dissipation capability of the radiator (12) when the opening / closing means (26) opens the bypass passage (25).

  Thus, during the defrosting operation in which the opening / closing means (26) opens the bypass passage (25), the high-temperature refrigerant discharged from the first compression mechanism (11a) is reliably supplied to the suction-side evaporator (16) for suction. The side evaporator (16) can be defrosted.

According to a twenty-seventh aspect of the present invention, in the ejector-type refrigeration cycle according to any one of the twenty-second to twenty- sixth aspects, the refrigerant passage extends from the first branch portion (18) outlet side to the nozzle portion (13a) inlet side. The high pressure side pressure reduction means (17) which is arrange | positioned and decompresses and expands the refrigerant | coolant which flowed out from the heat radiator (12) is characterized by the above-mentioned.

  According to this, during the normal operation in which the opening / closing means (26) closes the bypass passage (25), the refrigerant flowing into the nozzle part (13a) becomes a gas-liquid two-phase refrigerant by the action of the high pressure side pressure reducing means (17). Can be depressurized. Therefore, compared with the case where the liquid refrigerant is introduced into the nozzle part (13a), the boiling of the refrigerant in the nozzle part (13a) can be promoted to improve the nozzle efficiency.

  As a result, the amount of pressure increase in the diffuser section (13d) can be increased to further improve the COP. Further, by configuring the high-pressure side pressure reducing means (17) with a variable throttle mechanism, it is possible to change the flow rate of the refrigerant flowing into the nozzle portion (13a) according to the cycle load fluctuation. Furthermore, even if load fluctuation occurs, the cycle can be stably operated while exhibiting high COP.

The invention according to claim 28 is the ejector-type refrigeration cycle according to any one of claims 22 to 27 , which is disposed between the suction-side evaporator (16) and the second compression mechanism (21a). A suction-side gas-liquid separator (22) for separating the gas-liquid refrigerant, and the gas-phase refrigerant outlet of the suction-side gas-liquid separator (22) is connected to the suction port side of the second compression mechanism (21a). It is characterized by being.

  According to this, even if the liquid refrigerant flows out from the suction side evaporator (16) or the high-temperature refrigerant condenses during the defrosting operation of the suction side evaporator (16), the suction side gas-liquid separator Since only the gas-phase refrigerant separated in (22) can be supplied to the second compression mechanism (21a), the problem of liquid compression of the second compression mechanism (21a) can be avoided.

In the invention according to claim 29 , the first compression mechanism (11a) that compresses and discharges the refrigerant, and the branch portion (38) that branches the flow of the high-pressure refrigerant discharged from the first compression mechanism (11a). And the first radiator (121) that radiates one of the refrigerants branched at the branch part (38), and the refrigerant that flows out of the first radiator (121) is injected from the nozzle part (13a) that decompresses and expands. The refrigerant is sucked from the refrigerant suction port (13b) by the flow of the high-speed jet refrigerant, and the mixed refrigerant of the jet refrigerant and the suction refrigerant sucked from the refrigerant suction port (13b) is boosted by the diffuser section (13d). An ejector (13), a second radiator (122) that radiates heat of the other refrigerant branched by the branch portion (38), and a suction side pressure reducing means for decompressing and expanding the refrigerant flowing out of the second radiator (122) (19) and suction The suction side evaporator (16) that evaporates the refrigerant flowing out from the decompression means (19) and flows out to the refrigerant suction port (13b) side, and the suction side evaporator (16) outlet side refrigerant are sucked and compressed, The second compression mechanism (21a) that discharges to the refrigerant suction port (13b) side, the bypass passage (25) that guides the high-pressure side refrigerant of the cycle to the suction-side evaporator (16), and the bypass passage (25) are opened and closed. It is characterized by an ejector refrigeration cycle having an opening / closing means (26).

  According to this, during the normal operation in which the opening / closing means (26) closes the bypass passage (25), the heat exchange capability (heat dissipation capability) of the first radiator (121) and the second radiator (122) is changed independently. Therefore, for example, the heat exchange capability of the second radiator (122) and the heat exchange capability (endothermic performance) of the suction side evaporator (16) 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 (13a) of an ejector (13) 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 (13a) can be increased, and COP can be improved.

  Furthermore, in the normal operation, even if the operating condition is such that the suction capacity of the ejector (13) decreases with a decrease in the flow rate of the drive flow of the ejector (13), the ejector is similar to the invention according to claim 1. The refrigerating cycle can be stably operated in a state where a high COP is exhibited.

  That is, by increasing the suction pressure of the first compression mechanism (11a) by the pressure increasing action of the diffuser part (13d), not only the compressor driving power of the first compression mechanism (11a) is reduced, but also the respective first Since the pressure difference between the suction pressure and the discharge pressure of the first and second compression mechanisms (11a, 21a) can be reduced, the compression efficiency of the first and second compression mechanisms (11a, 21a) can be improved.

  As a result, even if the flow rate fluctuation of the driving flow occurs and the boosting capability of the diffuser section (13d) decreases, the ejector refrigeration cycle can be stably operated in a state where a high COP is exhibited.

  In addition, when frosting occurs in the suction side evaporator (16), the opening / closing means (26) is opened, so that the high-temperature refrigerant discharged from the first compression mechanism (11a) is directly taken into the suction side evaporator (16). ) To be defrosted and defrosted. Therefore, it is possible to avoid the cycle failure due to the frost formation of the suction side evaporator (16), and to stably operate the ejector refrigeration cycle.

According to a twenty- ninth aspect of the present invention, the ejector refrigeration cycle according to the thirty-sixth aspect further includes an outflow side evaporator (14) for evaporating the refrigerant that has flowed out of the diffuser section (13d). According to this, during the normal operation in which the opening / closing means (26) closes the bypass passage (25), not only the suction side evaporator (16) but also the outflow side evaporator (14) can exhibit the refrigerating capacity.

The invention described in claim 31 is the ejector refrigeration cycle according to claim 30 , further comprising an auxiliary bypass passage (25a) for guiding the high-pressure side refrigerant of the cycle to the outflow-side evaporator (14). To do. According to this, the high-temperature refrigerant | coolant discharged from the 1st compression mechanism (11a) can be guide | induced to an outflow side evaporator (14), and can be defrosted.

32. In the ejector refrigeration cycle according to any one of claims 29 to 31 , as in the invention according to claim 32 , the high-pressure side refrigerant of the cycle includes a first radiator (121) and a second radiator ( 122) An upstream side refrigerant, wherein the bypass passage (25) bypasses the first radiator (121) and the second radiator (122) to evaporate the refrigerant upstream of the radiator (12) on the suction side. It may lead to the vessel (16).

Further, as in the invention described in claim 33 , the first heat dissipating capacity adjusting means (121a) for adjusting the heat dissipating capacity of the first heat dissipator (121) is provided, and the high-pressure side refrigerant of the cycle is the first heat dissipator ( 121) A downstream side refrigerant, and the first heat radiation capacity adjusting means (121a) is configured so that the bypass passage (25) guides the refrigerant on the downstream side of the first radiator (121) to the suction side evaporator (16). The heat dissipation capability of the first radiator (121) may be reduced.

Furthermore, as in the invention described in claim 34 , the second heat dissipating capacity adjusting means (122a) for adjusting the heat dissipating capacity of the second heat dissipator (122) is provided. 122) A downstream side refrigerant, the second heat radiation capacity adjusting means (122a), when the bypass passage (25) guides the refrigerant on the downstream side of the first radiator (122) to the suction side evaporator (16). The heat dissipation capability of the first radiator (122) may be reduced.

Furthermore, as in the invention described in claim 35 , the first and second heat radiation capacity adjusting means (121a, 122a) for adjusting the heat radiation capacity of the first and second heat radiators (121, 122) are provided. The high-pressure side refrigerant is a refrigerant on the downstream side of at least one of the first and second radiators (122), and the first and second heat radiation capacity adjusting means (121a, 122a) are bypass passages (25). However, when the refrigerant on the downstream side of the first radiator (122) is guided to the suction side evaporator (16), the heat radiation capability of the first and second radiators (121, 122) may be reduced. .

  Thus, during the defrosting operation in which the opening / closing means (26) opens the bypass passage (25), the high-temperature refrigerant discharged from the first compression mechanism (11a) is reliably supplied to the suction-side evaporator (16) for suction. The side evaporator (16) can be defrosted.

The invention according to claim 36, in the ejector type refrigeration cycle according to any one of claims 29 to 35, when the opening and closing means (26) which closes the bypass passage (25), a second radiator ( 122) and an internal heat exchanger (30) for exchanging heat between the refrigerant flowing out of 122) and the low-pressure side refrigerant of the cycle.

  According to this, the enthalpy difference (refrigeration capacity) between the enthalpy of the inlet side refrigerant and the enthalpy of the outlet side refrigerant can be increased and the COP can be improved.

  Specifically, the low-pressure side refrigerant of the cycle may be a refrigerant sucked into the first compression mechanism (11a) as in the invention described in claim 44, or as in the invention described in claim 45. Alternatively, the refrigerant may be sucked into the second compression mechanism (21a).

According to the invention of claim 39 , in the ejector type refrigeration cycle according to any one of claims 29 to 38 , the refrigerant passage extending from the outlet side of the first radiator (121) to the inlet side of the nozzle part (13a) is provided. The high pressure side pressure reduction means (17) which is arrange | positioned and decompresses and expands the refrigerant | coolant which flowed out from the 1st heat radiator (121) is characterized by the above-mentioned.

  According to this, during the normal operation in which the opening / closing means (26) closes the bypass passage (25), the refrigerant flowing into the nozzle part (13a) becomes a gas-liquid two-phase refrigerant by the action of the high pressure side pressure reducing means (17). Can be depressurized. Therefore, compared with the case where the liquid refrigerant is introduced into the nozzle part (13a), the boiling of the refrigerant in the nozzle part (13a) can be promoted to improve the nozzle efficiency.

  As a result, the amount of pressure increase in the diffuser section (13d) can be increased to further improve the COP. Further, by configuring the high-pressure side pressure reducing means (17) with a variable throttle mechanism, it is possible to change the flow rate of the refrigerant flowing into the nozzle portion (13a) according to the cycle load fluctuation. As a result, even when load fluctuation occurs, the cycle can be stably operated while exhibiting a high COP.

According to a 40th aspect of the present invention, in the ejector refrigeration cycle according to any one of the 29th to 39th aspects, the ejector refrigeration cycle is disposed between the suction side evaporator (16) and the second compression mechanism (21a). A suction-side gas-liquid separator (22) for separating the gas-liquid refrigerant, and the gas-phase refrigerant outlet of the suction-side gas-liquid separator (22) is connected to the suction port side of the second compression mechanism (21a). It is characterized by being.

  According to this, even if the liquid refrigerant flows out from the suction side evaporator (16) or the high-temperature refrigerant condenses during the defrosting operation of the suction side evaporator (16), the suction side gas-liquid separator Since only the gas-phase refrigerant separated in (22) can be supplied to the second compression mechanism (21a), the problem of liquid compression of the second compression mechanism (21a) can be avoided.

In the invention according to claim 41 , in the ejector refrigeration cycle according to any one of claims 1 to 40 , first discharge capacity changing means (11b) for changing the refrigerant discharge capacity of the first compression mechanism (11a). ) And second discharge capacity changing means (21b) for changing the refrigerant discharge capacity of the second compression mechanism (21a). The first discharge capacity changing means (11b) and the second discharge capacity changing means (21b) The refrigerant discharge capacities of the first compression mechanism (11a) and the second compression mechanism (21a) can be changed independently of each other.

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

According to the invention of claim 42 , in the ejector refrigeration cycle according to any one of claims 1 to 41 , the first compression mechanism (11a) and the second compression mechanism (21a) are in the same housing. It is accommodated and it is comprised integrally. Accordingly, the first compression mechanism (11a) and the second compression mechanism (21a) can be reduced in size, and the entire ejector refrigeration cycle can be reduced in size.

As in the invention described in claim 43 , in the ejector-type refrigeration cycle according to any one of claims 1 to 42 , the first compression mechanism (11a) is configured to increase the pressure of the refrigerant until it becomes equal to or higher than the critical pressure. It may be.

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

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

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

  A radiator 12 is connected to the discharge port side of the first compressor 11. The heat dissipator 12 heat-exchanges the high-pressure refrigerant discharged from the first compressor 11 and the outside air (outside air) blown by the cooling fan 12a to dissipate the high-pressure refrigerant and cool it. It is. 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.

  And with the increase / decrease in the amount of blowing air by this rotation speed control, the heat dissipation capability of the radiator 12 also increases / decreases. Furthermore, when the cooling fan 12a is stopped, the radiator 12 of the present embodiment is in a state in which it hardly exhibits the heat dissipation capability. Therefore, the cooling fan 12a of the present embodiment constitutes a heat dissipation capacity adjusting means for adjusting the heat dissipation capacity of the radiator 12.

  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.

  Further, a receiver (liquid receiver) as a high-pressure side gas-liquid separator that separates the gas-liquid refrigerant flowing out of the radiator 12 and stores excess liquid-phase refrigerant may be provided on the outlet side of the radiator 12. Good. Then, the saturated liquid phase refrigerant separated from the receiver may be led to the downstream side.

  An ejector 13 is connected to the outlet side of the radiator 12. The ejector 13 is a refrigerant decompression unit that decompresses and expands the refrigerant, and is also a refrigerant circulation unit that circulates the refrigerant by suction of a refrigerant flow ejected at high speed.

  Specifically, the ejector 13 reduces the passage area of the high-pressure refrigerant that has flowed out of the radiator 12 so as to communicate with the nozzle portion 13a that decompresses and expands the high-pressure refrigerant isentropically, and the refrigerant injection port of the nozzle portion 13a. And a refrigerant suction port 13b for sucking the refrigerant discharged from the second compressor 21 described later.

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

  The diffuser portion 13d is formed in a shape that gradually increases the refrigerant passage area, and functions to increase the refrigerant pressure by decelerating the refrigerant flow, that is, to convert the velocity energy of the refrigerant into pressure energy. Further, an accumulator 15 is connected to the outlet side of the diffuser portion 13d.

  The accumulator 15 is an outflow-side gas-liquid separator that separates the gas-liquid refrigerant flowing out of the diffuser portion 13d and stores excess liquid-phase refrigerant in the cycle. The suction port of the first compressor 11 is connected to the gas-phase refrigerant outlet of the accumulator 15, and the suction-side evaporator 16 is connected to the liquid-phase refrigerant outlet via an electric variable throttle mechanism 19. ing.

  The variable throttle mechanism 19 is a suction-side decompression unit that further decompresses and expands the liquid refrigerant flowing out of the accumulator 15. More specifically, the variable throttle mechanism 19 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.

  Further, the variable throttle mechanism 19 can fully close the throttle opening of the valve body. Thereby, the distribution | circulation of the refrigerant | coolant between the liquid phase refrigerant | coolant outflow port of the accumulator 15 and the suction side evaporator 16 inlet side can be interrupted | blocked. The operation of the variable aperture mechanism 19 is controlled by a control signal output from the control device.

  The suction-side evaporator 16 evaporates the low-pressure refrigerant and exhibits a heat absorption effect by exchanging heat between the low-pressure refrigerant decompressed and expanded by the variable throttle mechanism 19 and the freezer air circulated and blown by the blower fan 16a. This is an endothermic heat exchanger. Therefore, in this embodiment, the air in a freezer becomes a 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.

  The suction port of the second compressor 21 is connected to the outlet side of the suction side evaporator 16. The basic configuration of the second compressor 21 is the same as that of the first compressor 11. Accordingly, the second compressor 21 is an electric compressor that drives the fixed capacity type second compression mechanism 21a by the second electric motor 21b. Furthermore, the second electric motor 21b of the present embodiment constitutes a second discharge capacity changing means for changing the refrigerant discharge capacity of the second compression mechanism 21a.

  Further, as described above, the refrigerant suction port 13 b of the ejector 13 is connected to the discharge port of the second compressor 21.

  Further, the ejector refrigeration cycle 100 of the present embodiment includes a first compression mechanism 11a between the discharge port side and the radiator 12 inlet side, and a variable throttle mechanism 19 outlet side and a suction side evaporator 16 inlet side. A bypass passage 25 for connecting the two is provided. Therefore, the bypass passage 25 constitutes a refrigerant flow path that guides the high-pressure refrigerant in the upstream side of the radiator 12 discharged from the first compression mechanism 11 a to the suction-side evaporator 16 by bypassing the radiator 12. Yes.

  The bypass passage 25 is provided with an opening / closing valve 26 as an opening / closing means for opening / closing the bypass passage 25. The opening / closing valve 26 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.

  As described above, the reason for adopting the on-off valve with a pressure reducing function having the pressure reducing function as the on-off valve 26 is not only to ensure the pressure difference between the pressure of the first compressor 11 inlet side refrigerant and the outlet side refrigerant pressure, This is because if the high-pressure refrigerant discharged from the first compressor 11 flows directly into the suction side evaporator 16, there is a concern that the refrigerant pressure in the suction side evaporator 16 may exceed the pressure resistance of the suction side evaporator 16. is there.

  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 16 is reduced until it becomes lower than the pressure resistance capability of the suction side evaporator 16. .

  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.

  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, 16a, 21b, 26 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. The second discharge capacity control means for controlling the heat discharge function and the function as the heat radiation capacity control means for controlling the operation of the cooling fan 12a as the heat radiation capacity adjustment means are also provided.

  Of course, you may comprise a 1st discharge capability control means, a 2nd discharge capability control means, and a thermal radiation capability control means with a different control apparatus.

  Further, the control device includes an outside air sensor for detecting the outside air temperature, a detected value of a sensor group (not shown) such as an inside temperature sensor for detecting the inside temperature, an operation switch for operating the refrigerator, a normal operation mode and a defrosting. Various operation signals of an operation panel (not shown) provided with a changeover switch for switching between operation modes are input.

  Next, the operation of the present embodiment in the above configuration will be described with reference to FIG. In the ejector refrigeration cycle 100 of the present embodiment, it is possible to switch between a normal operation mode for cooling the interior and a defrosting operation mode for defrosting the suction side evaporator 16. FIG. 2A is a Mollier diagram in the normal operation mode, and FIG. 2B is a Mollier diagram in the defrosting operation mode.

  First, the normal operation mode will be described. The normal operation mode is executed when the operation switch of the operation panel is turned on and the changeover switch is switched to the normal operation mode.

When the normal operation mode is executed, the control device operates the first and second electric motors 11b and 21b, the cooling fan 12a, and the blower fan 16a. Thus, the first compressor 11 sucks the refrigerant, compressing and discharging (a ₂ points in FIG. 2 (a)). Further, the control device adjusts the throttle opening degree of the variable throttle mechanism 19 so that the refrigerant evaporation temperature in the suction side evaporator 16 becomes a predetermined temperature, and the on-off valve 26 is closed.

The high-temperature and high-pressure gas-phase refrigerant discharged from the first compressor 11 flows into the radiator 12 without flowing into the bypass passage 25 because the on-off valve 26 is closed, and the cooling fan 12a. The heat is exchanged with the blown air (outside air) blown from the heat to dissipate and condense (a ₂ points → b ₂ points). The refrigerant radiated by the radiator 12 flows into the nozzle portion 13a of the ejector 13 and is decompressed and expanded in an isentropic manner (b ₂ point → c ₂ point).

  And the pressure energy of a refrigerant | coolant is converted into speed energy at the time of this decompression | expansion expansion, and a refrigerant | coolant is injected at high speed from the refrigerant | coolant injection port of the nozzle part 13a. Due to the refrigerant suction action of the injected refrigerant, the refrigerant discharged from the second compressor 21 is sucked from the refrigerant suction port 13b.

Furthermore, the refrigerant injected from the nozzle part 13a and the refrigerant sucked from the refrigerant suction port 13b are mixed in the mixing part 13c of the ejector 13 and flow into the diffuser part 13d (c ₂ point → d ₂ point, j ₂ points → d ₂ points). In the diffuser portion 13d, the refrigerant pressure energy rises (d ₂ point → e ₂ point) because the velocity energy of the refrigerant is converted into pressure energy due to the expansion of the passage area.

Next, the refrigerant flowing out of the diffuser portion 13d flows into the accumulator 15 and is separated into a gas phase refrigerant and a liquid phase refrigerant (e ₂ point → f ₂ point and e ₂ point → g ₂ point). The gas-phase refrigerant that has flowed out from the gas-phase refrigerant outlet of the accumulator 15 is sucked into the first compressor 11 and compressed again (point f ₂ → a ₂ ).

On the other hand, the liquid-phase refrigerant that has flowed out from the outlet of the liquid-phase refrigerant of the accumulator 15 is further decompressed and expanded isoenthalpically by the variable throttle mechanism 19 to reduce its pressure (g ₂ point → h ₂ point). Variable decompressed and expanded refrigerant is at the diaphragm mechanism 19, and flows into the suction side evaporator 16, the blower fan 16a is evaporated by absorbing heat from the internal air circulated blown (h ₂ points → i ₂ points). Thereby, the air in a warehouse is cooled.

The refrigerant flowing out of the suction side evaporator 16 is sucked into the second compressor 21 and compressed (i ₂ point → j ₂ point). At this time, the control device controls the operations of the first and second electric motors 11b and 21b so that the COP of the ejector refrigeration cycle 100 as a whole approaches the maximum. Specifically, in order to improve the mechanical efficiency of the first and second compression mechanisms 11a and 21a, the first and second compression mechanisms 11a and 21a are controlled so that the pressure increase amounts are substantially equal.

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

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

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

  Next, the defrosting operation mode will be described. The defrosting operation mode is executed when the changeover switch is switched to the defrosting operation mode in a state where the operation switch of the operation panel is turned on.

When the defrosting operation mode is executed, the control device operates the first and second electric motors 11b and 21b. Thus, the first compressor 11 sucks the refrigerant, compressed to discharge (k ₂ points Figure 2 (b)). Further, the control device sets the throttle opening of the variable throttle mechanism 19 to a fully closed state, opens the on-off valve 26, and stops the cooling fan 12a and the blower fan 16a.

  The refrigerant discharged from the first compressor 11 flows into the bypass passage 25 because the on-off valve 26 is in the open state. At this time, in the present embodiment, the first compressor 11 → bypass with respect to the pressure loss of the refrigerant circuit circulating in the order of the first compressor 11 → the radiator 12 → the ejector 13 → the accumulator 15 → the first compressor 11. Since the pressure loss of the refrigerant circuit extending from the passage 25 → the suction side evaporator 16 → the second compressor 21 is set small, most of the refrigerant discharged from the first compressor 11 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 first compressor 11 flows out only to the radiator 12 side and is removed. In the frost operation mode, the refrigerant flow path may be switched so that the refrigerant discharged from the first compressor 11 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.

When the high-temperature and high-pressure refrigerant flowing into the bypass passage 25 passes through the on-off valve 26, it is decompressed and expanded in an enthalpy manner (k ₂ point → l ₂ 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 16 without flowing into the accumulator 15 side because the throttle opening of the variable throttle mechanism 19 is fully closed.

The refrigerant that has flowed into the suction-side evaporator 16 dissipates the amount of heat to the suction-side evaporator 16 (l ₂ point → m ₂ point). As a result, the suction side evaporator 16 is defrosted. The refrigerant that has dissipated heat in the suction side evaporator 16 is sucked into the second compressor 21 and compressed (m ₂ point → n ₂ point).

The refrigerant discharged from the second compressor 21 is depressurized by the pressure loss when passing through the refrigerant suction port 13b → mixing part 13c → diffuser part 13d of the ejector and flows into the accumulator 15 (n ₂ point → o _2). point). The gas-phase refrigerant flowing out from the gas-phase refrigerant outlet of the accumulator 15 is sucked into the first compressor 11 and compressed again (o ₂ point → k ₂ point).

  Since the ejector refrigeration cycle 100 of the present embodiment operates as described above, the following excellent effects can be obtained.

  First, in the normal operation mode, for example, when the outside air temperature is low, the operating condition is such that the pressure difference between the high-pressure refrigerant and the low-pressure refrigerant decreases and the drive flow of the ejector 13 decreases, that is, the ejector 13 Even under the operating conditions in which the suction ability of the ejector 13 decreases, the suction ability of the ejector 13 can be assisted by the action of the second compression mechanism 21a.

  The liquid refrigerant can be reliably supplied from the accumulator 15 to the suction side evaporator 16 by the suction action of the second compression mechanism 21a. Thereby, the density fall of the refrigerant | coolant which flows out from the diffuser part 13d of the ejector 13 → the gaseous-phase refrigerant | coolant exit of the accumulator 15, and is suck | inhaled by the 1st compressor mechanism 11a can be suppressed.

  As a result, a decrease in the flow rate of the drive flow of the ejector 13 can be suppressed, and the ejector refrigeration cycle can be operated stably.

  In addition, since the pressure of the refrigerant can be increased by the pressure increasing action of the two first and second compression mechanisms 11a and 21a and the diffuser portion 13d of the ejector 13, the first and second compression mechanisms can be used for the case where the pressure of the refrigerant is increased by one compression mechanism. 2 COP can be improved by reducing the driving power of the compression mechanisms 11a and 21a.

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

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

  Further, since the saturated gas phase refrigerant can be sucked into the first compression mechanism 11a from the gas phase refrigerant outlet of the accumulator 15, the refrigerant in the first compression mechanism 11a is compared with the case where the gas phase refrigerant having a superheat degree is sucked. Can be compressed in the isentropic manner.

  Therefore, a refrigeration cycle apparatus having a large pressure difference between the high-pressure refrigerant and the low-pressure refrigerant, for example, a refrigeration cycle apparatus that reduces the refrigerant evaporation temperature of the suction side evaporator 16 to an extremely low temperature such as −30 to −10 ° C. as in the present embodiment. Therefore, COP can be improved extremely effectively.

  In addition, when frosting occurs in the suction side evaporator 16, the control device opens the on-off valve 26 so that the high-temperature refrigerant discharged from the first compressor 11 flows directly into the suction side evaporator 16. A defrosting operation mode for defrosting can be executed. Accordingly, it is possible to avoid the cycle failure due to the frost formation of the suction side evaporator 16 and to stably operate the ejector refrigeration cycle 100.

  Furthermore, since the variable throttle mechanism 19 is employed as the pressure reducing means and the throttle opening of the variable throttle mechanism 19 is fully closed during the defrosting operation, it is ensured that the refrigerant flowing out of the bypass passage 25 flows to the accumulator 15 side. Can be prevented.

  Note that a fixed throttle such as an orifice or a capillary tube may be employed as the pressure reducing means. The reason for this is that even when a fixed throttle is employed, the pressure loss of the suction side evaporator 16 is sufficiently small relative to the pressure loss of the fixed throttle, and further, the bypass by the suction action of the second compressor 21 This is because almost the entire amount of the refrigerant that has flowed out of the passage 25 can flow into the suction side evaporator 16.

(Second Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 3, the fixed throttle 19a and the check valve 19b are adopted instead of the variable throttle mechanism 19 with respect to the ejector refrigeration cycle 100 of the first embodiment. An example will be described. In FIG. 3, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.

  The fixed throttle 19a is a suction-side decompression unit that further decompresses and expands the liquid-phase refrigerant that has flowed out of the accumulator 15. Specifically, an orifice, a capillary tube, or the like can be employed. The check valve 19b prohibits the refrigerant flowing out of the bypass passage 25 from flowing to the accumulator 15 side. Other configurations are the same as those of the first embodiment.

  When the ejector refrigeration cycle 100 of this embodiment is operated, it operates similarly to the Mollier diagram of FIG. 2 of the first embodiment both in the normal operation mode and in the defrosting operation mode. Furthermore, since the check valve 19b is employed, it is possible to reliably prevent the refrigerant flowing out of the bypass passage 25 from flowing to the accumulator 15 side in the defrosting operation mode. Therefore, the same effect as the first embodiment can be obtained.

  In addition, if the check valve 19b is a check valve integrated with a pressure reducing mechanism that has a sufficiently small refrigerant passage area when the valve is opened, the fixed throttle 19a can be eliminated. In this case, the check valve integrated with the pressure reducing mechanism serves both as the function of the suction side pressure reducing means and the function of prohibiting the refrigerant flowing out of the bypass passage 25 from flowing to the accumulator 15 side.

(Third embodiment)
In the present embodiment, as illustrated in the overall configuration diagram of FIG. 4, an example in which the connection mode of the bypass passage 25 is changed with respect to the first embodiment will be described. Specifically, the bypass passage 25 of the present embodiment is provided between the radiator 12 outlet side and the nozzle portion 13a inlet side of the ejector 13, and between the variable throttle mechanism 19 outlet side and the suction side evaporator 16 inlet side. It is provided to connect between them.

  Therefore, the bypass passage 25 constitutes a refrigerant flow path that guides the high-pressure refrigerant of the cycle downstream of the radiator 12 to the suction-side evaporator 16.

  When the ejector refrigeration cycle 100 of the present embodiment is operated, the normal operation mode operates in the same manner as the Mollier diagram of FIG. 2A of the first embodiment. On the other hand, in the defrosting operation mode, since the control device stops the cooling fan 12 a, the refrigerant discharged from the first compressor 11 does not radiate heat at the radiator 12. For this reason, also in the defrosting operation mode, it operates similarly to the Mollier diagram of FIG. 2B of the first embodiment. Therefore, the same effect as the first embodiment can be obtained.

(Fourth embodiment)
In the present embodiment, an example in which a gas-liquid separator 22 is added to the first embodiment will be described as shown in the overall configuration diagram of FIG. The gas-liquid separator 22 is a suction-side gas-liquid separator that separates the gas-liquid refrigerant flowing out from the suction-side evaporator 16 and accumulates excess refrigerant in the cycle.

  When the ejector-type refrigeration cycle 100 of this embodiment is operated, it operates similarly to the Mollier diagram of FIG. 2 of the first embodiment both in the normal operation mode and in the defrosting operation mode. Therefore, the same effect as the first embodiment can be obtained.

  Furthermore, even if the liquid refrigerant flows out of the suction side evaporator 16 during the normal operation mode or the high-temperature refrigerant flowing into the suction side evaporator 16 condenses during the defrosting operation mode, the gas-liquid separator Since only the gas-phase refrigerant separated in 22 can be supplied to the second compressor 21, the problem of liquid compression of the second compressor 21 can be avoided.

(Fifth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 6, an example in which the defrosting operation mode is realized by eliminating the bypass passage 25 and the on-off valve 26 with respect to the first embodiment will be described. Other configurations are the same as those of the first embodiment. When the ejector refrigeration cycle 100 of the present embodiment is operated, it operates as shown in the Mollier diagram of FIG. 7A in the normal operation mode.

  The operation in the normal operation mode is the same as the operation in the normal operation mode of the first embodiment (FIG. 2A). In addition, the code | symbol which shows the state of the refrigerant | coolant in FIG. 7 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.

  On the other hand, in the defrosting operation mode, the control device operates the first and second electric motors 11b and 21b, the cooling fan 12a, and the blower fan 16a, and further, the throttle opening degree of the variable throttle mechanism 19 is set higher than that in the normal operation mode. increase.

  Accordingly, as shown in FIG. 7B, the refrigerant state in the defrosting operation mode changes in the same manner as in the normal operation mode, but the refrigerant evaporation pressure in the suction side evaporator 16 can be defrosted, that is, The refrigerant evaporation temperature can be raised to a temperature higher than 0 ° C.

  Therefore, in the defrosting operation mode of the present embodiment, the refrigerant evaporation temperature in the suction side evaporator 16 can be increased and the suction side evaporator 16 can be defrosted. Furthermore, in the normal operation mode, the same effects as in the normal operation mode of the first embodiment can be obtained.

(Sixth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 8, an electric heater 16b is provided as a heating means for heating the suction side evaporator 16, as compared with the fifth embodiment. The electric heater 16b generates heat when electric power is supplied from the control device, and can be composed of a PTC element, nichrome wire, or the like. Other configurations are the same as those of the first embodiment.

  When the ejector refrigeration cycle 100 of the present embodiment is operated, the normal operation mode operates in the same manner as the Mollier diagram of FIG. 2A of the first embodiment. On the other hand, in the defrosting operation mode, the control device stops the first and second electric motors 11b and 21b, the cooling fan 12a, and the blower fan 16a and energizes the electric heater 16b.

  Accordingly, in the defrosting operation mode, the suction side evaporator 16 can be heated and defrosted by the heat generated by the electric heater 16b. Further, in the normal operation mode, the ejector refrigeration cycle 100 can be stably operated as in the first embodiment, and the COP can be effectively improved as the whole ejector refrigeration cycle.

(Seventh 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. Accordingly, in FIG. 9, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  In the ejector refrigeration cycle 200, a temperature type expansion valve 17 is connected to the outlet side of the radiator 12 as high pressure side decompression means for decompressing and expanding the high pressure refrigerant flowing out of the radiator 12. More specifically, the temperature type expansion valve 17 of the present embodiment is disposed in the refrigerant passage from the radiator 12 outlet side to the branching portion 18 inlet side described later.

  The temperature type expansion valve 17 has a temperature sensing part (not shown) arranged in an outlet side refrigerant passage of the outflow side evaporator 14 described later, and the temperature and pressure of the outflow side evaporator 14 outlet side refrigerant. Based on the above, a variable throttle that detects the degree of superheat of the refrigerant on the outlet side of the outlet evaporator 14 and adjusts the valve opening (refrigerant flow rate) by a mechanical mechanism so that the degree of superheat becomes a predetermined value set in advance. Mechanism.

  A branch portion 18 is connected to the outlet side of the temperature expansion valve 17 to branch the flow of the intermediate pressure refrigerant flowing out of the temperature expansion valve 17. The branch portion 18 is configured by a three-way joint having three inflow / outflow ports, and 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 18 is connected to the nozzle portion 13a side of the ejector 13, and the other refrigerant outlet is connected to the refrigerant suction port 13b side of the ejector 13. Further, an outlet-side evaporator 14 is connected to the outlet side of the diffuser portion 13d of the ejector 13.

  The outflow side evaporator 14 heat-exchanges the refrigerant that flows out of the diffuser portion 13d of the ejector 13 and the air in the refrigerator that is circulated and blown by the blower fan 14a, thereby evaporating the low-pressure refrigerant and exerting an endothermic effect. It is a heat exchanger. Therefore, the heat exchange target fluid in the outflow side evaporator 14 is the air in the refrigerator.

  The blower fan 14a is an electric blower whose rotation speed (amount of blown air) is controlled by a control voltage output from the control device. The suction port of the first compressor 11 is connected to the refrigerant outlet side of the outflow side evaporator 14.

  Further, the suction side evaporator 16 is connected to the other refrigerant outlet of the branch portion 18 via an electric variable throttle mechanism 19 which is a suction side pressure reducing means. The suction port of the second compressor 21 is connected to the outlet side of the suction side evaporator 16, and the refrigerant suction port 13 b of the ejector 13 is connected to the discharge port of the second compressor 21.

  Further, in the ejector refrigeration cycle 200 of the present embodiment, similarly to the first embodiment, the suction between the discharge side of the first compression mechanism 11a and the inlet side of the radiator 12 and the outlet side of the variable throttle mechanism 19 is sucked. A bypass passage 25 for connecting the side evaporator 16 to the inlet side is provided. The bypass passage 25 is provided with an opening / closing valve 26 as an opening / closing means for opening / closing the bypass passage 25.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. FIG. 10A is a Mollier diagram in the normal operation mode, and FIG. 10B is a Mollier diagram in the defrosting operation mode. First, the normal operation mode will be described. The normal operation mode is executed when the operation switch of the operation panel is turned on and the changeover switch is switched to the normal operation mode.

When the normal operation mode is executed, the control device operates the first and second electric motors 11b and 21b, the cooling fan 12a, and the blower fans 14a and 16a. Thus, the first compressor 11 sucks the refrigerant, compressing and discharging (a ₁₀ point in FIG. 10 (a)). Further, the control device adjusts the throttle opening degree of the variable throttle mechanism 19 so that the refrigerant evaporation temperature in the suction side evaporator 16 becomes a predetermined temperature, and the on-off valve 26 is closed.

The high-temperature and high-pressure gas-phase refrigerant discharged from the first compressor 11 flows into the radiator 12 and the blown air (outside air) blown from the cooling fan 12a because the on-off valve 26 is closed. Heat exchange with heat to condense and condense (a ₁₀ points → b ₁₀ points). Refrigerant flowing out of the radiator 12, flows into the thermal expansion valve 17, isenthalpic depressurize expands the gas-liquid two-phase state (b ₁₀ points → c ₁₀ points).

At this time, the opening degree of the temperature type expansion valve 17 is adjusted so that the degree of superheat (g ₁₀ points) of the refrigerant on the outlet side of the outlet evaporator 14 becomes a predetermined value. The intermediate pressure refrigerant flowing out of the temperature type expansion valve 17 flows into the branching portion 18 and is divided into a refrigerant flow flowing into the nozzle portion 13a side of the ejector 13 and a refrigerant flow flowing into the refrigerant suction port 13b side of the ejector 13. The

  Here, in this embodiment, when the throttle opening degree of the variable throttle mechanism 19 is adjusted so that the refrigerant evaporation temperature in the suction side evaporator 16 becomes a predetermined temperature, the refrigerant flow rate flowing into the nozzle portion 13a side. The flow rate characteristic (pressure loss characteristic) of the nozzle portion 13a is such that the flow rate ratio Ge / Gnoz between Gnoz and the refrigerant flow rate Ge flowing into the refrigerant suction port 13b becomes an optimum flow rate ratio that can exhibit a high COP as a whole cycle. It has been decided.

The intermediate-pressure refrigerant flowing from the branch portion 18 to the nozzle part 13a side is isentropically depressurized expanded in the nozzle portion 13a ₍₁₀ points → d ₁₀ points c). And the pressure energy of a refrigerant | coolant is converted into speed energy at the time of this decompression | expansion expansion, and a refrigerant | coolant is injected at high speed from the refrigerant | coolant injection port of the nozzle part 13a. Due to the refrigerant suction action of the injected refrigerant, the refrigerant discharged from the second compressor 21 is sucked from the refrigerant suction port 13b.

Further, the refrigerant injected from the nozzle part 13a and the refrigerant sucked from the refrigerant suction port 13b are mixed in the mixing part 13c of the ejector 13 and flow into the diffuser part 13d (d ₁₀ points → e ₁₀ points, j ₁₀ points → e ₁₀ points). The expansion of the passage area in the diffuser portion 13d, since the velocity energy of refrigerant is converted into pressure energy, the pressure of the refrigerant is increased (e ₁₀ points → f ₁₀ points).

Then, refrigerant flowing from the diffuser portion 13d flows into the discharge side evaporator 14, the air blowing fan 14a by such refrigerant is evaporated by absorbing heat from the circulating blower has been refrigerator air (f ₁₀ points → g ₁₀ points). Thereby, the air in a refrigerator is cooled. The refrigerant flowing from the discharge side evaporator 14 is sucked into the first compressor 11, it is compressed again (g ₁₀ points → a _10-point).

On the other hand, intermediate-pressure refrigerant flowing from the branch portion 18 to the refrigerant suction port 13b side, the variable throttle is isenthalpic depressurize expansion further in mechanism 19 lowers its pressure ₍₁₀ c → h _10). Variable decompressed and expanded refrigerant is at the diaphragm mechanism 19, and flows into the suction side evaporator 16, absorbs heat from the freezer in air circulated blown by the blower fan 16a evaporates (h ₁₀ points → i ₁₀ points). Thereby, the air in a freezer is cooled.

The refrigerant flowing out of the suction side evaporator 16 is sucked into the second compressor 21 and compressed (i ₁₀ points → j ₁₀ points). At this time, the control device controls the operations of the first and second electric motors 11b and 21b in the same manner as in the first embodiment so that the COP of the ejector refrigeration cycle 200 as a whole approaches the maximum. Moreover, the refrigerant discharged from the second compressor 21, as described above, is drawn from the refrigerant suction port 13b into the ejector 13 (j ₁₀ points → e ₁₀ points).

  Next, the defrosting operation mode will be described. The defrosting operation mode is executed when the changeover switch is switched to the defrosting operation mode in a state where the operation switch of the operation panel is turned on.

When the defrosting operation mode is executed, the control device operates the first and second electric motors 11b and 21b. Thus, the first compressor 11 sucks the refrigerant, compressing and discharging (k ₁₀ points in Figure 10 (b)). Further, the control device sets the throttle opening of the variable throttle mechanism 19 to a fully closed state, opens the on-off valve 26, and stops the cooling fan 12a and the blower fans 14a and 16a.

The high-temperature and high-pressure gas-phase refrigerant discharged from the first compressor 11 flows into the bypass passage 25 as in the first embodiment because the on-off valve 26 is in the open state, and the on-off valve 26 When passing through, it expands under reduced pressure in an isenthalpy manner (k ₁₀ points → l ₁₀ points).

  The high-temperature and low-pressure gas-phase refrigerant that has passed through the on-off valve 26 is sucked without flowing into the branching portion 18 side through the variable throttle mechanism 19 because the throttle opening of the variable throttle mechanism 19 is fully closed. It flows into the side evaporator 16.

The refrigerant that has flowed into the suction-side evaporator 16 dissipates heat to the suction-side evaporator 16 (l ₁₀ points → m ₁₀ points). As a result, the suction side evaporator 16 is defrosted. The refrigerant that has dissipated heat in the suction side evaporator 16 is sucked into the second compressor 21 and compressed (m ₁₀ points → n ₁₀ points).

The refrigerant discharged from the second compressor 21 is depressurized by the pressure loss when passing through the refrigerant suction port 13b → the mixing unit 13c → the diffuser unit 13d of the ejector and flows into the outflow side evaporator 14 (n ₁₀ points). → o ₁₀ points).

The refrigerant that has flowed into the outflow side evaporator 14 dissipates the amount of heat to the outflow side evaporator 14 (o ₁₀ point → p ₁₀ point). Thereby, the defrosting of the outflow side evaporator 14 is made. The refrigerant that has dissipated heat in the outflow evaporator 14 is sucked into the first compressor 11 and compressed again (p ₁₀ points → k ₁₀ points).

  Since the ejector refrigeration cycle 200 of the present embodiment operates as described above, the following effects can be exhibited.

  (A) In the normal operation mode, since the flow of the refrigerant is divided so that the flow rate ratio Ge / Gnoz becomes the optimum flow rate ratio in the branch portion 18, both the outflow side evaporator 14 and the suction side evaporator 16 The refrigerant can be supplied appropriately. Therefore, both the outflow side evaporator 14 and the suction side evaporator 16 can exhibit a cooling action simultaneously.

  At this time, the refrigerant evaporation pressure of the suction side evaporator 16 becomes the pressure after the pressure is increased by the diffuser portion 13 d and then further reduced by the variable throttle mechanism 19, and the refrigerant evaporation pressure of the outflow side evaporator 14 is the pressure of the suction side evaporator 16. The refrigerant evaporation pressure becomes the pressure after being increased by the second compressor 21 and the diffuser unit 13d.

  Therefore, the refrigerant evaporation pressure (refrigerant evaporation temperature) of the suction side evaporator 16 can be made sufficiently lower than the refrigerant evaporation pressure (refrigerant evaporation temperature) of the outflow side evaporator 14. As a result, the outflow evaporator 14 can be used for cooling in a low-temperature refrigerator, and the suction-side evaporator 16 can be used for cooling in a cryogenic freezer.

  (B) In the normal operation mode, the second compressor 21 (second compression) even if the operation condition is such that the drive flow of the ejector 13 decreases, that is, the suction condition of the ejector 13 decreases. By the action of the mechanism 21a), as in the first embodiment, the ejector refrigeration cycle 200 as a whole can be stably operated in a state where a high COP is exhibited.

  (C) In the normal operation mode, the refrigerant flows in the order of the first compressor 11 → the radiator 12 → the branching portion 18 → the ejector 13 → the outflow side evaporator 14 → the first compressor 11, and further the first compressor 11 → The refrigerant flows in the order of radiator 12 → branching section 18 → variable throttle mechanism 19 → suction side evaporator 16 → second compressor 11 → ejector 13 → outflow side evaporator 14 → first compressor 11.

  That is, since the flow of the refrigerant passing through the evaporator such as the outflow side evaporator 14 and the suction side evaporator 16 is annular, lubricating oil (refrigerator oil) for the first and second compressors 11 and 21 is used as the refrigerant. Even if mixed, it is possible to prevent the oil from staying in the outflow side evaporator 14 and the suction side evaporator 16.

  (D) In the normal operation mode, the temperature type expansion valve 17 which is a variable throttle mechanism is employed as the high pressure side pressure reducing means, so that the flow rate of the refrigerant flowing into the nozzle portion 13a of the ejector 13 is changed according to the cycle load fluctuation. Can be changed. As a result, even when load fluctuation occurs, the cycle can be stably operated while exhibiting a high COP.

(E) to the normal operation mode, refrigerant reduced in pressure by the thermal expansion valve 17 (c ₁₀ points in FIG. 10) because the gas-liquid two-phase state, a gas-liquid two-phase state to the nozzle portion 13a of the ejector 13 A refrigerant can be introduced. Therefore, the boiling of the refrigerant in the nozzle portion 13a can be promoted and the nozzle efficiency can be improved as compared with the case where the liquid phase refrigerant is caused to flow into the nozzle portion 13a.

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

  Further, when frost formation occurs in the outflow side evaporator 14 and the suction side evaporator 16, the control device opens the on-off valve 26 so that the high-temperature refrigerant discharged from the first compressor 11 is removed from the suction side evaporator. It is possible to execute a defrosting operation mode in which the defrosting is performed by flowing into the refrigerant 16 and the high-temperature refrigerant discharged from the second compressor 21 is caused to flow into the outflow evaporator 14 to defrost.

  Therefore, it is possible to stably operate the ejector-type refrigeration cycle 200 while avoiding a cycle failure due to frost formation on the outflow side evaporator 14 and the suction side evaporator 16. Furthermore, since the variable throttle mechanism 19 is employed as the pressure reducing means and the throttle opening degree of the variable throttle mechanism 19 is fully closed during the defrosting operation, the refrigerant flowing out of the bypass passage 25 is branched via the variable throttle mechanism 19. It is possible to reliably prevent the flow to the 18 side.

(Eighth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 11, an example in which the connection mode of the bypass passage 25 is changed with respect to the seventh embodiment will be described.

  Specifically, the bypass passage 25 of the present embodiment is provided between the radiator 12 outlet side and the temperature type expansion valve 17 inlet side, and between the variable throttle mechanism 19 outlet side and the suction side evaporator 16 inlet side. Are provided to connect. Therefore, the bypass passage 25 constitutes a refrigerant flow path that guides the high-pressure refrigerant of the cycle downstream of the radiator 12 to the suction-side evaporator 16.

  When the ejector refrigeration cycle 200 of the present embodiment is operated, the normal operation mode operates in the same manner as the Mollier diagram of FIG. 10A of the seventh embodiment. On the other hand, in the defrosting operation mode, since the control device stops the cooling fan 12 a, the refrigerant discharged from the first compressor 11 does not radiate heat at the radiator 12. For this reason, also in the defrosting operation mode, it operates similarly to the Mollier diagram of FIG. 10B of the first embodiment.

  Therefore, the same effect as that of the seventh embodiment can be obtained also in the ejector refrigeration cycle 200 of the present embodiment.

(Ninth embodiment)
In the present embodiment, an example in which a gas-liquid separator 22 is added to the seventh embodiment will be described as shown in the overall configuration diagram of FIG. The gas-liquid separator 22 is a suction-side gas-liquid separator that separates the gas-liquid refrigerant flowing out from the suction-side evaporator 16 and accumulates excess refrigerant in the cycle.

  When the ejector refrigeration cycle 200 of this embodiment is operated, it operates in the same manner as the Mollier diagram of FIG. 10 of the seventh embodiment both in the normal operation mode and in the defrosting operation mode. Therefore, the same effect as that of the seventh embodiment can be obtained.

  Furthermore, even if the liquid refrigerant flows out of the suction side evaporator 16 during the normal operation mode or the high-temperature refrigerant flowing into the suction side evaporator 16 condenses during the defrosting operation mode, the gas-liquid separator Since only the gas-phase refrigerant separated in 22 can be supplied to the second compressor 21, the problem of liquid compression of the second compressor 21 can be avoided.

(10th Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 13, an auxiliary bypass passage 25 a that guides the high-pressure refrigerant discharged from the first compression mechanism 11 a to the outflow side evaporator 14 is added to the seventh embodiment. An example will be described.

  More specifically, the auxiliary bypass passage 25a of the present embodiment includes the bypass passage 25 on the downstream side of the on-off valve 26 in the defrosting operation mode, the diffuser portion 13d outlet side and the outlet side evaporator 14 of the ejector 13. It is a refrigerant flow path connecting between the inlet side.

  Further, the auxiliary bypass passage 25a is provided with an auxiliary bypass passage check valve 25b that prohibits the refrigerant flowing out of the diffuser portion 13d of the ejector 13 from flowing toward the bypass passage 25 in the normal operation mode.

  Instead of the auxiliary bypass passage check valve 25b, an auxiliary bypass passage opening / closing valve that opens and closes the auxiliary bypass passage 25a may be employed. In this case, the auxiliary bypass passage opening / closing valve may be closed in the normal operation mode, and the auxiliary bypass passage opening / closing valve may be opened in the defrosting operation mode.

  Therefore, when the ejector refrigeration cycle 200 of this embodiment is operated, it operates as shown in the Mollier diagram of FIG. 14A in the normal operation mode. The operation in the normal operation mode is the same as the operation in the normal operation mode of the seventh embodiment (FIG. 10A). In addition, the code | symbol which shows the state of the refrigerant | coolant in FIG. 14 uses the same code | symbol as the code | symbol which shows the state of the same refrigerant | coolant in FIG. 10, and has changed only the subscript. The same applies to the Mollier diagrams described in the 11th to 25th embodiments described later.

On the other hand, in the defrosting operation mode, the high-temperature and high-pressure gas-phase refrigerant discharged from the first compressor 11 has the open / close valve 26 opened, so that the bypass passage 25 is similar to the seventh embodiment. When the gas flows into and passes through the on-off valve 26, it is decompressed and expanded in an isoenthalpy manner (k ₁₄ point → l ₁₄ point). The refrigerant flow depressurized by the on-off valve 26 is divided into a refrigerant flow flowing toward the suction-side evaporator 16 and a refrigerant flow flowing toward the auxiliary bypass passage 25a.

The high-temperature and low-pressure gas-phase refrigerant that has flowed out from the on-off valve 26 toward the suction-side evaporator 16 radiates the amount of heat to the suction-side evaporator 16 (l ₁₄ points → m ₁₄ points). As a result, the suction side evaporator 16 is defrosted. The refrigerant radiated by the suction side evaporator 16 is sucked into the second compressor 21 and compressed (m ₁₄ points → n ₁₄ points).

The refrigerant discharged from the second compressor 21 is depressurized due to the pressure loss when passing through the refrigerant suction port 13b → mixing part 13c → diffuser part 13d of the ejector (n ₁₄ points → o ₁₄ points). The refrigerant that has flowed out of the diffuser portion 13d merges with the refrigerant that has flowed out of the auxiliary bypass passage 25a and flows into the outflow side evaporator 14 (o ₁₄ point → o ′ ₁₄ point, l ₁₄ point → o ′ ₁₄ point).

Furthermore, the refrigerant that has flowed into the outflow evaporator 14 dissipates the amount of heat to the outflow evaporator 14 (o ′ ₁₄ point → p ₁₄ point). Thereby, the defrosting of the outflow side evaporator 14 is made. The refrigerant having released heat in the discharge side evaporator 14 is compressed again is sucked into the first compressor 11 (p ₁₄ points → k ₁₄ points).

  Since the ejector refrigeration cycle 200 of the present embodiment operates as described above, the same effects as those of the seventh embodiment can be obtained in the normal operation mode. Furthermore, in the defrosting operation mode, not only the same effect as in the seventh embodiment can be obtained, but also the pressure of the refrigerant flowing into the outflow side evaporator 14 is reduced to protect the outflow side evaporator 14. You can also.

  That is, in this embodiment, the pressure of the refrigerant flowing into the outflow evaporator 14 can be reduced by joining the refrigerant flowing out from the diffuser portion 13d with the refrigerant flowing out from the auxiliary bypass passage 25a.

  Therefore, it is possible to prevent the refrigerant pressure in the outflow side evaporator 14 from exceeding the pressure resistance of the outflow side evaporator 14 and to protect the outflow side evaporator 14. Further, as described above, since the refrigerant pressure in the outflow side evaporator 14 can be reduced, the refrigerant pressure (refrigerant temperature) in the suction side evaporator 16 is increased within the allowable pressure resistance of the suction side evaporator 16. You may let them.

(Eleventh embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 15, an example will be described in which the defrosting operation mode is realized by eliminating the bypass passage 25 and the on-off valve 26 with respect to the seventh embodiment. When the ejector refrigeration cycle 200 of the present embodiment is operated, it operates as shown in the Mollier diagram of FIG. 16A in the normal operation mode.

  The operation in the normal operation mode is the same as the operation in the normal operation mode of the seventh embodiment (FIG. 10A). On the other hand, in the defrosting operation mode, the control device operates the first and second electric motors 11b and 21b, the cooling fan 12a, and the blower fan 16a, and further, the throttle opening degree of the variable throttle mechanism 19 is set higher than that in the normal operation mode. increase.

  Thereby, as shown in FIG. 16B, the refrigerant state in the defrosting operation mode changes in the same manner as in the normal operation mode, but the refrigerant evaporation pressure in the suction side evaporator 16 can be defrosted, that is, The refrigerant evaporation temperature can be raised to a temperature higher than 0 ° C.

  Therefore, in the defrosting operation mode of the present embodiment, the refrigerant evaporation temperature in the suction side evaporator 16 can be increased and the suction side evaporator 16 can be defrosted. Furthermore, in the normal operation mode, the same effects as in the normal operation mode of the seventh embodiment can be obtained.

  Furthermore, if an electric expansion valve is employed instead of the temperature expansion valve 17 and the control device increases the throttle opening of the electric expansion valve in the defrosting operation mode, the outflow side evaporator The refrigerant evaporation temperature at 14 can also be increased.

(Twelfth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 17, the outflow-side evaporator 14 and the blower fan 14 a are eliminated from the ejector refrigeration cycle 200 of the seventh embodiment. Furthermore, an example in which the accumulator 15 is added to the outlet side of the diffuser portion 13d of the ejector 13 and the internal heat exchanger 30 is added will be described.

  The internal heat exchanger 30 performs heat exchange between the refrigerant flowing out of the radiator 12 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. . More specifically, the refrigerant that has flowed out of the radiator 12 in the present embodiment is a refrigerant that circulates in the refrigerant passage from the branch portion 18 outlet side to the variable throttle mechanism 19 inlet side, and the cycle low-pressure side refrigerant is 2 Refrigerant sucked into the compression mechanism 21a.

  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.

  Further, in the present embodiment, the temperature type expansion valve 17 that is a high pressure side pressure reducing means is provided in the refrigerant passage from the radiator 12 outlet side to one refrigerant outlet side of the branch part 18 to the nozzle part 13a inlet side of the ejector 13. It is arranged. Other configurations are the same as those of the seventh embodiment.

  Next, the operation of the present embodiment will be described based on the Mollier diagram of FIG. FIG. 18A is a Mollier diagram in the normal operation mode, and FIG. 18B is a Mollier diagram in the defrosting operation mode.

First, the normal operation mode will be described. In the normal operation mode, the first compressor 11 discharge refrigerant (a ₁₈ point in FIG. 18 (a)) is, the heat radiation to be condensed by the radiator 12 (a ₁₈ point → b ₁₈ points). The refrigerant that has flowed out of the radiator 12 flows into the branch portion 18 and is divided into a refrigerant flow that flows into the nozzle portion 13 a side of the ejector 13 and a refrigerant flow that flows into the refrigerant suction port 13 b side of the ejector 13.

As in the seventh embodiment, the high-pressure refrigerant that has flowed out from the branch portion 18 toward the nozzle portion 13a flows in the order of the temperature expansion valve 17 → the nozzle portion 13a of the ejector 13 → the diffuser portion 13 of the ejector 13 (b ₁₈ points → c ₁₈ points → d ₁₈ points → e ₁₈ points → f ₁₈ points). The refrigerant flowing out of the diffuser section 13d is gas-liquid separated by the accumulator 15, and the separated gas-phase refrigerant is sucked into the first compressor 11 and compressed again (f ₁₈ point → g ₁₈ point → a ₁₈ point).

On the other hand, the high-pressure refrigerant that has flowed out from the branch portion 18 toward the refrigerant suction port 13b decreases its enthalpy in the internal heat exchanger 30 (b ₁₈ → b ′ ₁₈ points). The refrigerant flowing out from the high-pressure side refrigerant flow path 30a of the internal heat exchanger 30 flows in the order of the variable throttle mechanism 19 → the suction-side evaporator 16 (b ′ ₁₈ points → h ₁₈ points → i) as in the seventh embodiment. ₁₈ points).

The refrigerant flowing out of the suction side evaporator 16 increases its enthalpy in the internal heat exchanger 30 (i ₁₈ points → i ′ ₁₈ points). The refrigerant flowing out from the low-pressure side refrigerant flow path 30b of the internal heat exchanger 30 is sucked into the second compressor 21, compressed, and sucked from the refrigerant suction port 13b of the ejector 13 (i ′ ₁₈ points → j ₁₈ Point → e ₁₈ points).

Next, the defrosting operation mode will be described. In the defrosting operation mode, the high-temperature and high-pressure gas-phase refrigerant discharged from the first compressor 11 flows into the bypass passage 25 because the on-off valve 26 is open, and the on-off valve 26 is When passing, it expands under reduced pressure in an isenthalpy manner (k ₁₈ points → l ₁₈ points).

  The high-temperature and low-pressure gas-phase refrigerant that has passed through the on-off valve 26 is sucked without flowing into the branching portion 18 side through the variable throttle mechanism 19 because the throttle opening of the variable throttle mechanism 19 is fully closed. It flows into the side evaporator 16.

The refrigerant that has flowed into the suction-side evaporator 16 dissipates the amount of heat to the suction-side evaporator 16 (l ₁₈ points → m ₁₈ points). As a result, the suction side evaporator 16 is defrosted. The refrigerant radiated by the suction side evaporator 16 is sucked into the second compressor 21 and compressed (m ₁₈ point → n ₁₈ point).

The refrigerant discharged from the second compressor 21 is reduced in pressure by the pressure loss when passing through the refrigerant suction port 13b → mixing part 13c → diffuser part 13d of the ejector (n ₁₈ → o ₁₈ points), and the first compressor 11 is inhaled and compressed again (o ₁₈ points → k ₁₈ points).

  Therefore, when the ejector refrigeration cycle 200 of the present embodiment is operated, in the normal operation mode, the cooling action can be exerted by the suction side evaporator 16, and the same effects as (B) to (E) of the seventh embodiment. Can be obtained.

  Further, during the normal operation mode, the temperature type expansion valve 17 is disposed in the refrigerant passage from the radiator 12 outlet side to the refrigerant outlet side of one of the branch parts 18 to the nozzle part 13a inlet side of the ejector 13. In the branch part 18, the flow of the refrigerant or liquid refrigerant having a very low dryness can be branched.

  Therefore, in the case where the flow of the gas-liquid two-phase refrigerant in which the gas-phase refrigerant and the liquid-phase refrigerant are mixed in an inhomogeneous state is branched at the branching portion 18, both refrigerant outlets of the branching portion 18 are used. It becomes easy to make the state of the refrigerant flowing out from the same state. As a result, the flow rate ratio Ge / Gnoz of the refrigerant branched at the branching portion 18 can be easily brought close to the optimum flow rate ratio, and the COP can be further improved.

  Furthermore, during the normal operation mode, the enthalpy of the refrigerant flowing into the suction side evaporator 16 can be reduced by the action of the internal heat exchanger 30 as compared with the seventh 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 16 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, the high-pressure refrigerant flowing through the refrigerant passage from the branching section 18 outlet side to the variable throttle mechanism 19 inlet side and the low-pressure refrigerant sucked into the second compression mechanism 21a are heated. Since they are exchanged, the enthalpy of the refrigerant flowing from the branch portion 18 to the nozzle portion 13a 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 13a can be increased by unnecessarily reducing the enthalpy of the refrigerant flowing into the nozzle portion 13a.

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

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

  Further, since the accumulator 15 is arranged on the suction side of the first compressor 11, the problem of liquid compression of the first compressor 11 can be avoided.

  In addition, when frost formation occurs in the suction side evaporator 16, the control device opens the on-off valve 26 so that the high-temperature refrigerant discharged from the first compressor 11 flows into the suction side evaporator 16 and is removed. A defrosting operation mode for frosting can be executed. Therefore, similarly to the seventh embodiment, it is possible to avoid the cycle failure due to the frost formation of the suction side evaporator 16, and to stably operate the ejector refrigeration cycle 200.

(13th Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 19, an example in which the connection mode of the bypass passage 25 is changed with respect to the twelfth embodiment will be described.

  Specifically, the bypass passage 25 of the present embodiment connects between the radiator 12 outlet side and the branch portion 18 inlet side, and between the variable throttle mechanism 19 outlet side and the suction side evaporator 16 inlet side. It is provided to do. Therefore, the bypass passage 25 constitutes a refrigerant flow path that guides the high-pressure refrigerant of the cycle downstream of the radiator 12 to the suction-side evaporator 16.

  When the ejector refrigeration cycle 200 of the present embodiment is operated, the normal operation mode operates in the same manner as the Mollier diagram of FIG. 18A of the twelfth embodiment. On the other hand, in the defrosting operation mode, since the control device stops the cooling fan 12 a, the refrigerant discharged from the first compressor 11 does not radiate heat at the radiator 12. For this reason, also in the defrosting operation mode, it operates similarly to the Mollier diagram of FIG. 18B of the twelfth embodiment.

  Therefore, the same effects as those of the twelfth embodiment can be obtained in the ejector refrigeration cycle 200 of the present embodiment.

(14th Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 20, an example will be described in which the defrosting operation mode is realized by eliminating the bypass passage 25 and the on-off valve 26 with respect to the twelfth embodiment. When the ejector refrigeration cycle 200 of the present embodiment is operated, it operates as shown in the Mollier diagram of FIG. 21A in the normal operation mode.

  The operation in the normal operation mode is the same as the operation in the normal operation mode of the twelfth embodiment (FIG. 18A). On the other hand, in the defrosting operation mode, the control device operates the first and second electric motors 11b and 21b, the cooling fan 12a, and the blower fan 16a, and further, the throttle opening degree of the variable throttle mechanism 19 is set higher than that in the normal operation mode. increase.

  Thereby, as shown in FIG. 21B, the refrigerant state in the defrosting operation mode changes in the same manner as in the normal operation mode, but the refrigerant evaporation pressure in the suction side evaporator 16 can be defrosted, that is, The refrigerant evaporation temperature can be raised to a temperature higher than 0 ° C.

  Therefore, in the defrosting operation mode of the present embodiment, the refrigerant evaporation temperature in the suction side evaporator 16 can be increased and the suction side evaporator 16 can be defrosted. Further, in the normal operation mode, the same effect as in the normal operation mode of the twelfth embodiment can be obtained.

(Fifteenth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 22, the temperature type expansion valve 17 is abolished with respect to the ejector refrigeration cycle 200 of the seventh embodiment, and further, the refrigerant flow downstream of the branch portion 18. An example will be described in which an auxiliary radiator 12e is provided that dissipates heat from the refrigerant that is disposed and flows into the variable throttle mechanism 19.

  The auxiliary radiator 12 is a heat-dissipating heat exchanger that further heats and cools the high-pressure refrigerant by exchanging heat between the high-pressure refrigerant flowing out of the radiator 12 and the outside air (outside air) blown by the cooling fan 12a. 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. 22, 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 seventh embodiment.

  Next, the operation of the present embodiment will be described based on the Mollier diagram of FIG. FIG. 23A is a Mollier diagram in the normal operation mode, and FIG. 23B is a Mollier diagram in the defrosting operation mode.

First, the normal operation mode will be described. In the normal operation mode, the first compressor 11 discharge refrigerant (a ₂₃ point in FIG. 23 (a)) is, the heat dissipation and condensed by the radiator 12, the gas-liquid two-phase state (a ₂₃ point → b ₂₃ point). This is because the heat exchange capability of the radiator 12 is reduced compared to the seventh embodiment described above.

The high-pressure refrigerant that has flowed out of the radiator 12 flows into the branch portion 18 and is divided into a refrigerant flow that flows into the nozzle portion 13 a side of the ejector 13 and a refrigerant flow that flows into the refrigerant suction port 13 b side of the ejector 13. The refrigerant that has flowed from the branch portion 18 to the nozzle portion 13 side of the ejector 13 flows in the order of the ejector 13 → the outflow side evaporator 14, and is compressed by the first compressor 11 (b ₂₃ point → d ₂₃ point → e ₂₃ points → f ₂₃ points → g ₂₃ points → a ₂₃ points).

On the other hand, high-pressure refrigerant flowing from the branch portion 18 to the refrigerant suction port 13b side is further cooled by the auxiliary radiator 12e, the liquid phase (b ₂₃ points → b _'23 points). Refrigerant flowing out of the auxiliary radiator 12e is in this order of the variable throttle mechanism 19 → the suction side evaporator 16, it is compressed is sucked from the refrigerant suction port 13b by the second compressor 21 (b _'23 points → h ₂₃ points → i ₂₃ points → j ₂₃ points → e ₂₃ points).

Next, the defrosting operation mode will be described. In the defrosting operation mode, it operates as shown in the Mollier diagram of FIG. The operation in this defrosting operation mode is the same as the operation in the defrosting operation mode of the seventh embodiment (FIG. 10B). Therefore, when the ejector refrigeration cycle 200 of this embodiment is operated, In the operation mode, the same effects as (A) to (C) of the seventh embodiment can be obtained.

  Furthermore, since the heat exchange capability of the radiator 12 is reduced during the normal operation mode, the enthalpy of the refrigerant flowing into the nozzle portion 13a is not unnecessarily reduced. Therefore, similarly to the twelfth embodiment, it is possible to obtain the COP improvement effect by not reducing the enthalpy of the refrigerant flowing into the nozzle portion 13a.

  Furthermore, during the normal operation mode, the enthalpy of the refrigerant flowing into the suction side evaporator 16 can be reduced by the action of the auxiliary radiator 12e. Thereby, the enthalpy difference of the enthalpy of the inlet side refrigerant | coolant of the suction side evaporator 16 and the enthalpy of the outlet side refrigerant | coolant can be expanded, refrigeration capacity can be increased, and COP can be improved further.

  Further, when frost formation occurs in the suction side evaporator 16, the same defrosting operation mode as that in the seventh embodiment can be executed, so that cycle failure due to frost formation of the suction side evaporator 16 can be avoided. Thus, the ejector refrigeration cycle 200 can be stably operated.

(Sixteenth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 24, an example in which the connection mode of the bypass passage 25 is changed with respect to the fifteenth embodiment will be described.

  Specifically, the bypass passage 25 of the present embodiment is provided between the auxiliary radiator 12e outlet side and the variable throttle mechanism 19 inlet side, and between the variable throttle mechanism 19 outlet side and the suction side evaporator 16 inlet side. Are provided to connect. Therefore, the bypass passage 25 constitutes a refrigerant flow path that guides the high-pressure refrigerant of the cycle downstream of the radiator 12 to the suction-side evaporator 16.

  When the ejector refrigeration cycle 200 of the present embodiment is operated, the normal operation mode operates in the same manner as the Mollier diagram of FIG. 23A of the fifteenth embodiment. On the other hand, in the defrosting operation mode, since the control device stops the cooling fan 12a, the refrigerant discharged from the first compressor 11 does not radiate heat at the radiator 12 and the auxiliary radiator 12e. For this reason, also in the defrosting operation mode, it operates similarly to the Mollier diagram of FIG. 23B of the fifteenth embodiment.

  Therefore, the same effect as that of the fifteenth embodiment can be obtained in the ejector refrigeration cycle 200 of the present embodiment.

(17th Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 25, an example in which the connection mode of the bypass passage 25 is changed with respect to the fifteenth embodiment will be described.

  Specifically, the bypass passage 25 of the present embodiment is between the radiator 12 outlet side and the auxiliary radiator 12e inlet side, and between the variable throttle mechanism 19 outlet side and the suction side evaporator 16 inlet side. It is provided to connect. Therefore, the bypass passage 25 constitutes a refrigerant flow path that guides the high-pressure refrigerant of the cycle downstream of the radiator 12 to the suction-side evaporator 16.

  When the ejector refrigeration cycle 200 of the present embodiment is operated, the normal operation mode operates in the same manner as the Mollier diagram of FIG. 23A of the fifteenth embodiment. On the other hand, in the defrosting operation mode, since the control device stops the cooling fan 12a, the refrigerant discharged from the first compressor 11 does not radiate heat at the radiator 12 and the auxiliary radiator 12e. For this reason, also in the defrosting operation mode, it operates similarly to the Mollier diagram of FIG. 23B of the fifteenth embodiment.

  Therefore, the same effect as that of the fifteenth embodiment can be obtained in the ejector refrigeration cycle 200 of the present embodiment.

(Eighteenth embodiment)
In this embodiment, an example in which a gas-liquid separator 22 is added to the fifteenth embodiment will be described as shown in the overall configuration diagram of FIG. The gas-liquid separator 22 is a suction-side gas-liquid separator that separates the gas-liquid refrigerant flowing out from the suction-side evaporator 16 and accumulates excess refrigerant in the cycle.

  When the ejector refrigeration cycle 200 of the present embodiment is operated, it operates similarly to the Mollier diagram of FIG. 23 of the fifteenth embodiment both in the normal operation mode and in the defrosting operation mode. Therefore, the same effect as that of the fifteenth embodiment can be obtained.

  Furthermore, even if the liquid refrigerant flows out of the suction side evaporator 16 during the normal operation mode or the high-temperature refrigerant flowing into the suction side evaporator 16 condenses during the defrosting operation mode, the gas-liquid separator Since only the gas-phase refrigerant separated in 22 can be supplied to the second compressor 21, the problem of liquid compression of the second compressor 21 can be avoided.

(Nineteenth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 27, an auxiliary bypass passage 25a for introducing the high-pressure refrigerant discharged from the first compression mechanism 11a to the outflow side evaporator 14 is added to the fifteenth embodiment. An example will be described. The basic configuration of the auxiliary bypass passage 25a and the auxiliary bypass passage check valve 25b provided in the auxiliary bypass passage 25a is the same as that of the tenth embodiment.

  Therefore, when the ejector refrigeration cycle 200 of the present embodiment is operated, it operates as shown in the Mollier diagram of FIG. 28A in the normal operation mode. The operation in the normal operation mode is the same as the operation in the normal operation mode of the fifteenth embodiment (FIG. 23 (a)). On the other hand, in the defrosting operation mode, it operates as shown in the Mollier diagram of FIG. The operation in the defrosting operation mode is the same as the operation in the defrosting operation mode of the tenth embodiment (FIG. 14B).

  Since the ejector refrigeration cycle 200 of the present embodiment operates as described above, the same effect as that of the fifteenth embodiment can be obtained in the normal operation mode, and in the defrosting operation mode, exactly the same as that of the tenth embodiment. Similar effects can be obtained.

(20th embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 29, an example will be described in which the defrosting operation mode is realized by eliminating the bypass passage 25 and the on-off valve 26 with respect to the fifteenth embodiment. When the ejector refrigeration cycle 200 of the present embodiment is operated, it operates as shown in the Mollier diagram of FIG. 30A in the normal operation mode.

  The operation in the normal operation mode is the same as that in FIG. 23A of the fifteenth embodiment. On the other hand, in the defrosting operation mode, the control device operates the first and second electric motors 11b and 21b, the cooling fan 12a, and the blower fan 16a, and further, the throttle opening degree of the variable throttle mechanism 19 is set higher than that in the normal operation mode. increase.

  Thereby, as shown in FIG. 30 (b), the refrigerant state in the defrosting operation mode changes in the same manner as in the normal operation mode, but the refrigerant evaporation pressure in the suction side evaporator 16 can be defrosted, that is, The refrigerant evaporation temperature can be raised to a temperature higher than 0 ° C.

  Therefore, in the defrosting operation mode of the present embodiment, the refrigerant evaporation temperature in the suction side evaporator 16 can be increased and the suction side evaporator 16 can be defrosted. Furthermore, in the normal operation mode, the same effects as in the normal operation mode of the fifteenth embodiment can be obtained.

(21st Embodiment)
In the present embodiment, an example in which an internal heat exchanger 31 and a check valve 19b are added to the ejector refrigeration cycle 200 of the seventh embodiment will be described as shown in the overall configuration diagram of FIG. The internal heat exchanger 31 is between the refrigerant in the decompression / expansion process passing through the throttle passage of the fixed throttle 19a serving as the high-pressure side refrigerant flow path and the second compression mechanism 21a suction refrigerant passing through the low-pressure side refrigerant flow path 31b. Heat exchange is performed.

  As a specific configuration of the internal heat exchanger 31, a double-tube heat exchanger configuration in which a fixed throttle 19a formed of a capillary tube or the like is arranged inside an outer tube forming the low-pressure side refrigerant flow path 31b. Adopted. Of course, a configuration in which the fixed throttle 19a and the refrigerant pipe forming the low-pressure side refrigerant flow path 31b are brazed and joined to exchange heat may be employed.

  Further, when the variable throttle mechanism 19 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 19. Can be adopted. Other configurations are the same as those of the seventh embodiment.

  Next, the operation of the present embodiment will be described based on the Mollier diagram of FIG. FIG. 32A is a Mollier diagram in the normal operation mode, and FIG. 32B is a Mollier diagram in the defrosting operation mode.

First, the normal operation mode will be described. In the normal operation mode, the action of the internal heat exchanger 31 increases the enthalpy of the second compression mechanism 21a suction-side refrigerant with respect to the seventh embodiment (i ₃₂ points → i ′ ₃₂ points in FIG. 32A). ), The enthalpy of the decompression / expansion process in the variable throttle mechanism 19 is reduced (b ₃₂ points → h ₃₂ points).

  In other words, the refrigerant passing through the fixed throttle 19a is cooled to the same temperature as the refrigerant sucked by the second compression mechanism 21a while expanding under reduced pressure, thereby reducing its enthalpy. Thereby, compared with 1st Embodiment, the enthalpy of the refrigerant | coolant which flows in into the outflow side evaporator 14 and the suction side evaporator 16 can be decreased. Other operations in the normal operation mode are the same as those in the seventh embodiment.

Next, the defrosting operation mode will be described. In the defrosting operation mode, the operation is performed as shown in the Mollier diagram of FIG. The operation in this defrosting operation mode is the same as the operation in the defrosting operation mode of the seventh embodiment (FIG. 10B). Therefore, when the ejector refrigeration cycle 200 of this embodiment is operated, In the operation mode, the same effects as (A) to (E) of the seventh embodiment can be obtained.

  Furthermore, the enthalpy of the refrigerant flowing into the suction side evaporator 16 can be reduced by the action of the internal heat exchanger 31 with respect to the seventh embodiment. Thereby, since the enthalpy difference of the enthalpy of the inlet side refrigerant | coolant of the suction side evaporator 16 and the enthalpy of the outlet side refrigerant | coolant can be expanded and a refrigerating capacity can be increased, COP can be improved further.

(Twenty-second embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 33, an example in which the connection mode of the bypass passage 25 is changed with respect to the twenty-first embodiment will be described.

  Specifically, the bypass passage 25 of the present embodiment is between the radiator 12 outlet side and the variable throttle mechanism 19 inlet side, and between the variable throttle mechanism 19 outlet side and the suction side evaporator 16 inlet side. It is provided to connect. Therefore, the bypass passage 25 constitutes a refrigerant flow path that guides the high-pressure refrigerant of the cycle downstream of the radiator 12 to the suction-side evaporator 16.

  When the ejector refrigeration cycle 200 of the present embodiment is operated, the normal operation mode operates in the same manner as the Mollier diagram of FIG. 32A of the 21st embodiment. On the other hand, in the defrosting operation mode, since the control device stops the cooling fan 12 a, the refrigerant discharged from the first compressor 11 does not radiate heat at the radiator 12. For this reason, it operates similarly to the Mollier diagram of FIG. 32 (b) of the 21st embodiment also in the defrosting operation mode.

  Therefore, the same effect as that of the twenty-first embodiment can be obtained in the ejector refrigeration cycle 200 of the present embodiment.

(23rd Embodiment)
This embodiment is an example in which an accumulator 14 and a gas-liquid separator 22 are added to the twenty-first embodiment as shown in the overall configuration diagram of FIG. When the ejector refrigeration cycle 200 of the present embodiment is operated, it operates similarly to the Mollier diagram of FIG. 32 of the 21st embodiment both in the normal operation mode and in the defrosting operation mode. Therefore, the same effect as that of the twenty-first embodiment can be obtained.

  Further, even if the liquid refrigerant flows out from the outflow side evaporator 14 in the normal operation mode or the high temperature refrigerant flowing into the outflow side evaporator 14 condenses in the defrosting operation mode, the accumulator 14 Since only the separated gas-phase refrigerant can be supplied to the first compressor 11, the problem of liquid compression of the first compressor 11 can be avoided.

  Furthermore, even if the liquid refrigerant flows out of the suction side evaporator 16 during the normal operation mode or the high-temperature refrigerant flowing into the suction side evaporator 16 condenses during the defrosting operation mode, the gas-liquid separator Since only the gas-phase refrigerant separated in 22 can be supplied to the second compressor 21, the problem of liquid compression of the second compressor 21 can be avoided.

(24th Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 35, an auxiliary bypass passage 25a that guides the high-pressure refrigerant discharged from the first compression mechanism 11a to the outflow side evaporator 14 is added to the twenty-first embodiment. An example will be described. The basic configuration of the auxiliary bypass passage 25a and the auxiliary bypass passage check valve 25b provided in the auxiliary bypass passage 25a is the same as that of the tenth embodiment.

  Therefore, when the ejector refrigeration cycle 200 of this embodiment is operated, it operates as shown in the Mollier diagram of FIG. 36A in the normal operation mode. The operation in the normal operation mode is the same as the operation in the normal operation mode of the twenty-first embodiment (FIG. 32 (a)). On the other hand, in the defrosting operation mode, it operates as shown in the Mollier diagram of FIG. The operation in the defrosting operation mode is the same as that in FIG. 14B of the tenth embodiment.

  Since the ejector refrigeration cycle 200 of the present embodiment operates as described above, the same effect as that of the 21st embodiment can be obtained in the normal operation mode, and in the defrosting operation mode, exactly the same as that of the 10th embodiment. Similar effects can be obtained.

(25th Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 37, an example in which the defrosting operation mode is realized by eliminating the bypass passage 25 and the on-off valve 26 from the twenty-first embodiment will be described. When the ejector refrigeration cycle 200 of the present embodiment is operated, the normal operation mode operates as shown in the Mollier diagram of FIG.

  The operation in the normal operation mode is the same as the operation in the normal operation mode of the twenty-first embodiment (FIG. 32 (a)). On the other hand, in the defrosting operation mode, the control device operates the first and second electric motors 11b and 21b, the cooling fan 12a, and the blower fan 16a, and further, the throttle opening degree of the variable throttle mechanism 19 is set higher than that in the normal operation mode. increase.

  As a result, as shown in FIG. 38 (b), the refrigerant state in the defrosting operation mode changes in the same manner as in the normal operation mode, but the refrigerant evaporation pressure in the suction side evaporator 16 can be defrosted, that is, The refrigerant evaporation temperature can be raised to a temperature higher than 0 ° C.

  Therefore, in the defrosting operation mode of the present embodiment, the refrigerant evaporation temperature in the suction side evaporator 16 can be increased and the suction side evaporator 16 can be defrosted. Furthermore, in the normal operation mode, the same effects as in the normal operation mode of the twenty-first embodiment can be obtained.

(26th Embodiment)
39 and 40, an example in which the ejector refrigeration cycle 300 of the present invention is applied to a refrigeration apparatus will be described. 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. 39 is an overall configuration diagram of the ejector refrigeration cycle 300 of the present embodiment.

  The ejector refrigeration cycle 300 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 FIG. 39, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  In the ejector refrigeration cycle 300, a temperature type expansion valve 17 is connected to the outlet side of the radiator 12 as high pressure side decompression means for decompressing and expanding the high pressure refrigerant flowing out of the radiator 12. The inlet side of the nozzle portion 13 a of the ejector 13 is connected to the outlet side of the temperature type expansion valve 17. Further, a branch portion 18 that branches the flow of the refrigerant flowing out of the diffuser portion 13d is connected to the outlet side of the diffuser portion 13d of the ejector 13.

  In the branch portion 18 of the present embodiment, the flow direction of the refrigerant flowing out from the one refrigerant outlet 18b to the outlet evaporator 14 side, and the flow of the refrigerant flowing out from the other refrigerant outlet 18c to the variable throttle mechanism 19 side. The direction is substantially Y-shaped so as to face the target direction and intersect at an acute angle with respect to the flow direction of the refrigerant flowing into the refrigerant inlet 18a from the diffuser portion 13d outlet side.

  Therefore, the refrigerant flowing into the branching portion 18 flows out from the branching portion 18 without unnecessarily reducing the flow velocity when the flow is branched. Thereby, the flow velocity (dynamic pressure) of the refrigerant flowing out from the ejector 15 at the branching portion 18 is maintained. Of course, the branch portion 18 is not limited to this, and may be formed in a substantially T-shape or the like.

  Further, the suction side evaporator 16 is connected to the other refrigerant outlet of the branch portion 18 via a variable throttle mechanism 19. The suction port of the second compressor 21 is connected to the outlet side of the suction side evaporator 16.

  Further, in the ejector refrigeration cycle 300 of the present embodiment, the suction between the first compression mechanism 11a outlet side and the radiator 12 inlet side, and the variable throttle mechanism 19 outlet side and the suction, as in the first embodiment. A bypass passage 25 for connecting the side evaporator 16 to the inlet side is provided. The bypass passage 25 is provided with an opening / closing valve 26 as an opening / closing means for opening / closing the bypass passage 25.

  Next, the operation of this embodiment in the above configuration will be described based on the Mollier diagram of FIG. 40A is a Mollier diagram in the normal operation mode, and FIG. 40B is a Mollier diagram in the defrosting operation mode. First, the normal operation mode will be described. The normal operation mode is executed when the operation switch of the operation panel is turned on and the changeover switch is switched to the normal operation mode.

When the normal operation mode is executed, the control device operates the first and second electric motors 11b and 21b, the cooling fan 12a, and the blower fans 14a and 16a. Thereby, the 1st compressor 11 suck | inhales a refrigerant | coolant, compresses and discharges ( _a40 point of Fig.40 (a)). Further, the control device adjusts the throttle opening degree of the variable throttle mechanism 19 so that the refrigerant evaporation temperature in the suction side evaporator 16 becomes a predetermined temperature, and the on-off valve 26 is closed.

The high-temperature and high-pressure gas-phase refrigerant discharged from the first compressor 11 flows into the radiator 12 and the blown air (outside air) blown from the cooling fan 12a because the on-off valve 26 is closed. Heat exchange with heat to condense and condense (a ₄₀ points → b ₄₀ points). The refrigerant flowing out of the radiator 12 flows into the temperature type expansion valve 17 and is decompressed and expanded in an enthalpy manner to be in a gas-liquid two-phase state (b ₄₀ points → c ₄₀ points).

At this time, the valve opening degree of the temperature type expansion valve 17 is adjusted so that the degree of superheat (g ₄₀ points) of the outlet side refrigerant 14 outlet side refrigerant becomes a predetermined value. The intermediate-pressure refrigerant flowing out of the thermal expansion valve 17, flows into the nozzle portion 13a of the ejector 13, isentropically decompressed to expand (c ₄₀ points → d ₄₀ points).

And the pressure energy of a refrigerant | coolant is converted into speed energy at the time of this decompression | expansion expansion, and a refrigerant | coolant is injected at high speed from the refrigerant | coolant injection port of the nozzle part 13a. Due to the refrigerant suction action of the injected refrigerant, the refrigerant discharged from the second compressor 21 is sucked from the refrigerant suction port 13b (j ₄₀ points → e ₄₀ points).

Furthermore, the suction refrigerant sucked from the injection refrigerant and the refrigerant suction port 13b that is injected from the nozzle portion 13a is mixed in the mixing portion 13c of the ejector 13, and flows into the diffuser portion 13d (d ₄₀ points → e ₄₀ points) . In the diffuser portion 13d, the passage energy is increased and the velocity energy of the refrigerant is converted into pressure energy, so that the pressure of the refrigerant increases (e ₄₀ points → f ₄₀ points).

  The refrigerant that has flowed out of the diffuser section 13d is split at the branch section 18 into a refrigerant flow that flows into the outflow evaporator 14 side and a refrigerant flow that flows into the variable throttle mechanism 19 side. Here, in the present embodiment, the refrigerant flowing into the outlet-side evaporator 14 side by setting the refrigerant passage area on the refrigerant outlet 18b side of the branching portion 18 larger than the refrigerant passage area on the refrigerant outlet 18c side. The flow rate G1 is set to be larger than the refrigerant flow rate G2 flowing into the variable throttle mechanism 19 side.

The refrigerant that has flowed into the outlet-side evaporator 14 from the branching section 18 absorbs heat from the air in the refrigerator circulated by the blower fan 14a and evaporates (f ₄₀ points → g ₄₀ points). Thereby, the air in a refrigerator is cooled. Then, the refrigerant flowing out from the outflow side evaporator 14 is sucked into the first compressor 11 and compressed again (g ₄₀ point → a ₄₀ point).

On the other hand, the refrigerant flowing into the variable throttle mechanism 19 from the branching portion 18 is further decompressed and expanded in an isenthalpy manner to reduce its pressure (c ₄₀ point → h ₄₀ point). Variable decompressed and expanded refrigerant is at the diaphragm mechanism 19, and flows into the suction side evaporator 16, the blower fan 16a is evaporated by absorbing heat from the freezer in air circulated blown (h ₄₀ points → i ₄₀ points). Thereby, the air in a freezer is cooled.

The refrigerant that has flowed out of the suction side evaporator 16 is sucked into the second compressor 21 and compressed (i ₄₀ points → j ₄₀ points). As described above, the refrigerant discharged from the second compressor 21 is sucked into the ejector 13 from the refrigerant suction port 13b (j ₄₀ points → e ₄₀ points).

  Next, the defrosting operation mode will be described. The defrosting operation mode is executed when the changeover switch is switched to the defrosting operation mode in a state where the operation switch of the operation panel is turned on. In the ejector refrigeration cycle 300 of this embodiment, two types of defrosting operation modes can be executed. In the defrosting operation mode of the present embodiment, the first defrosting operation mode is operated among the two types of defrosting operation modes. The second defrosting operation mode will be described later.

When the defrosting operation mode is executed, the control device operates the first and second electric motors 11b and 21b. Thus, the first compressor 11 sucks the refrigerant, compressing and discharging (k ₄₀ points in FIG. 40 (b)). Further, the control device sets the throttle opening of the variable throttle mechanism 19 to a fully closed state, opens the on-off valve 26, and stops the cooling fan 12a and the blower fans 14a and 16a.

Since the on-off valve 26 is in the open state, the high-temperature and high-pressure gas-phase refrigerant discharged from the first compressor 11 flows into the bypass passage 25 and passes through the on-off valve 26. It expands under reduced pressure enthalpy (k ₄₀ points → l ₄₀ points).

  The high-temperature and low-pressure gas-phase refrigerant that has passed through the on-off valve 26 is sucked without flowing into the branching portion 18 side through the variable throttle mechanism 19 because the throttle opening of the variable throttle mechanism 19 is fully closed. It flows into the side evaporator 16.

The refrigerant that has flowed into the suction-side evaporator 16 dissipates the amount of heat to the suction-side evaporator 16 (l ₁₀ points → m ₄₀ points). As a result, the suction side evaporator 16 is defrosted. The refrigerant radiated by the suction-side evaporator 16 is sucked into the second compressor 21 and compressed (m ₄₀ points → n ₄₀ points).

The refrigerant discharged from the second compressor 21 is depressurized by the pressure loss when passing through the refrigerant suction port 13b → the mixing unit 13c → the diffuser unit 13d of the ejector and flows into the outflow side evaporator 14 (n ₄₀ points). → o ₄₀ points).

The refrigerant that has flowed into the outflow evaporator 14 dissipates the amount of heat to the outflow evaporator 14 (o ₄₀ point → p ₄₀ point). Thereby, the defrosting of the outflow side evaporator 14 is made. The refrigerant that has dissipated heat in the outflow evaporator 14 is sucked into the first compressor 11 and compressed again (p ₄₀ points → k ₄₀ points).

  Since the ejector refrigeration cycle 300 of this embodiment operates as described above, the following effects can be exhibited.

  (A) In the normal operation mode, the flow of the refrigerant is divided at the branching portion 18 and the refrigerant is supplied to both the outflow side evaporator 14 and the suction side evaporator 16. Both side evaporators 16 can exhibit a cooling action simultaneously.

  At this time, the refrigerant evaporation pressure of the suction side evaporator 16 becomes the pressure after the pressure is increased by the diffuser portion 13 d and then further reduced by the variable throttle mechanism 19, and the refrigerant evaporation pressure of the outflow side evaporator 14 is the pressure of the suction side evaporator 16. The refrigerant evaporation pressure becomes the pressure after being increased by the second compressor 21 and the diffuser unit 13d.

  Therefore, the refrigerant evaporation pressure (refrigerant evaporation temperature) of the suction side evaporator 16 can be made sufficiently lower than the refrigerant evaporation pressure (refrigerant evaporation temperature) of the outflow side evaporator 14. As a result, the outflow evaporator 14 can be used for cooling in a low-temperature refrigerator, and the suction-side evaporator 16 can be used for cooling in a cryogenic freezer.

  (B) In the normal operation mode, the second compressor 21 (second compression) even if the operation condition is such that the drive flow of the ejector 13 decreases, that is, the suction condition of the ejector 13 decreases. By the action of the mechanism 21a), the ejector refrigeration cycle 300 as a whole can be stably operated in a state where a high COP is exhibited, as in the first embodiment.

  (C) In the normal operation mode, the refrigerant flow rate G1 flowing from the branch portion 18 to the outflow side evaporator 14 side is made larger than the refrigerant flow rate G2 flowing from the branch portion 18 to the variable throttle mechanism 19 side. More refrigerant 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.

  (D) In the normal operation mode, the temperature type expansion valve 17 which is a variable throttle mechanism is employed as the high pressure side pressure reducing means, so that the flow rate of the refrigerant flowing into the nozzle portion 13a of the ejector 13 is changed according to the cycle load fluctuation Can be changed. As a result, even if load fluctuation occurs, the cycle can be stably operated while exhibiting a high COP.

(E) to the normal operation mode, refrigerant reduced in pressure by the thermal expansion valve 17 (c ₄₀ points in FIG. 40) because the gas-liquid two-phase state, a gas-liquid two-phase state to the nozzle portion 13a of the ejector 13 A refrigerant can be introduced. Therefore, the boiling of the refrigerant in the nozzle portion 13a can be promoted and the nozzle efficiency can be improved as compared with the case where the liquid phase refrigerant is caused to flow into the nozzle portion 13a.

  Accordingly, the amount of recovered energy can be increased and the amount of pressure increase in the diffuser section 13d can be increased, so that the COP can be further improved. Furthermore, since the refrigerant passage area of the nozzle part 13a can be enlarged with respect to the case where the liquid phase refrigerant is caused to flow into the nozzle part 13a, the processing of the nozzle part 13a is facilitated. As a result, the manufacturing cost of the ejector 13 can be reduced, and the manufacturing cost of the ejector refrigeration cycle 300 as a whole can be reduced.

  Further, when frost formation occurs in the outflow side evaporator 14 and the suction side evaporator 16, the control device opens the on-off valve 26 so that the high-temperature refrigerant discharged from the first compressor 11 is removed from the suction side evaporator. It is possible to execute a defrosting operation mode in which the defrosting is performed by flowing into the refrigerant 16 and the high-temperature refrigerant discharged from the second compressor 21 is caused to flow into the outflow evaporator 14 to defrost.

  Therefore, it is possible to stably operate the ejector-type refrigeration cycle 200 while avoiding a cycle failure due to frost formation on the outflow side evaporator 14 and the suction side evaporator 16. Furthermore, since the variable throttle mechanism 19 is employed as the pressure reducing means and the throttle opening degree of the variable throttle mechanism 19 is fully closed during the defrosting operation, the refrigerant flowing out of the bypass passage 25 is branched via the variable throttle mechanism 19. It is possible to reliably prevent the flow to the 18 side.

  Here, defrosting in the second defrosting operation mode among the two types of defrosting operation modes described above will be described with reference to FIG. FIG. 40 (c) is a Mollier diagram of the second defrosting operation mode. The two types of defrosting operation modes can be appropriately selected according to the pressure resistance performance of the outflow side evaporator 14 and the suction side evaporator 16, for example.

  When the second defrosting operation mode is executed, similarly to the first defrosting operation mode, the control device operates the first and second electric motors 11b and 21b to open the on-off valve 26, and the cooling fan 12a and the blower fans 14a and 16a are stopped. Further, in the second defrosting operation mode, the control device fully opens the throttle opening of the variable throttle mechanism 19.

In the second defrosting operation mode, since the variable throttle mechanism 19 is in a fully open state, the flow of the refrigerant (1 ′ ₄₀ points) flowing out from the bypass passage 25 is the refrigerant flow flowing to the suction side evaporator 16 side, The refrigerant flow is divided into the refrigerant flow flowing toward the variable throttle mechanism 19 side.

The high-temperature and low-pressure gas-phase refrigerant that has flowed from the on-off valve 26 to the suction-side evaporator 16 side radiates the amount of heat to the suction-side evaporator 16 (1 ′ ₄₀ points → m ′ ₄₀ points). As a result, the suction side evaporator 16 is defrosted. The refrigerant radiated by the suction side evaporator 16 is sucked into the second compressor 21 and compressed (m ′ ₄₀ points → n ′ ₄₀ points).

The refrigerant discharged from the second compressor 21 is depressurized by pressure loss when passing through the refrigerant suction port 13b → mixing part 13c → diffuser part 13d of the ejector (n ′ ₄₀ points → o ′ ₄₀ points). Further, the refrigerant that has flowed out of the diffuser portion 13d merges with the refrigerant that has flowed out of the variable throttle mechanism 19 and flows into the outflow side evaporator 14 (n ′ ₄₀ points → o ″ ₄₀ points, l ′ ₄₀ points → o ″). ₄₀ points).

The refrigerant flowing into the outflow side evaporator 14 dissipates the amount of heat to the outflow side evaporator 14 (o ″ ₄₀ points → p ′ ₄₀ points), whereby the outflow side evaporator 14 is defrosted. The refrigerant radiated by the side evaporator 14 is sucked into the first compressor 11 and compressed again (p ′ ₄₀ points → k ′ ₄₀ points).

  According to the second defrosting operation mode, not only the outflow side evaporator 14 and the suction side evaporator 16 can be defrosted as in the first defrosting operation mode, but also the pressure of the refrigerant flowing into the outflow side evaporator 14 is reduced. It can also be lowered to protect the outflow side evaporator 14.

  That is, in the present embodiment, the pressure of the refrigerant flowing into the outflow side evaporator 14 can be reduced by joining the refrigerant flowing out from the diffuser portion 13d with the refrigerant flowing out from the variable throttle mechanism 19.

  Therefore, it is possible to prevent the refrigerant pressure in the outflow side evaporator 14 from exceeding the pressure resistance performance in the outflow side evaporator 14 and to protect the outflow side evaporator 14. Further, as described above, since the refrigerant pressure in the outflow side evaporator 14 can be reduced, the refrigerant pressure (refrigerant temperature) in the suction side evaporator 16 is increased within the allowable pressure resistance of the suction side evaporator 16. You may let them.

(27th Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 41, an example in which the connection mode of the bypass passage 25 is changed with respect to the twenty-sixth embodiment will be described.

  Specifically, the bypass passage 25 of the present embodiment is provided between the radiator 12 outlet side and the temperature type expansion valve 17 inlet side, and between the variable throttle mechanism 19 outlet side and the suction side evaporator 16 inlet side. Are provided to connect. Therefore, the bypass passage 25 constitutes a refrigerant flow path that guides the high-pressure refrigerant of the cycle downstream of the radiator 12 to the suction-side evaporator 16.

  When the ejector refrigeration cycle 300 of the present embodiment is operated, the normal operation mode operates in the same manner as the Mollier diagram of FIG. 40A of the 26th embodiment. On the other hand, in the defrosting operation mode, since the control device stops the cooling fan 12 a, the refrigerant discharged from the first compressor 11 does not radiate heat at the radiator 12. For this reason, also in the defrosting operation mode, it operates similarly to the Mollier diagram of FIG. 40 (b) of the 26th embodiment.

  Therefore, in this embodiment, the same effect as that in the 26th embodiment can be obtained. Of course, any of the first and second defrosting operation modes may be executed in the defrosting operation mode of the ejector refrigeration cycle 300 of the present embodiment.

(Twenty-eighth embodiment)
In the present embodiment, an example in which a gas-liquid separator 22 is added to the twenty-sixth embodiment will be described as shown in the overall configuration diagram of FIG. The gas-liquid separator 22 is a suction-side gas-liquid separator that separates the gas-liquid refrigerant flowing out from the suction-side evaporator 16 and accumulates excess refrigerant in the cycle.

  When the ejector refrigeration cycle 300 of this embodiment is operated, it operates similarly to the Mollier diagram of FIG. 40 of the 26th embodiment both in the normal operation mode and in the defrosting operation mode. Therefore, exactly the same effect as that in the 26th embodiment can be obtained.

  Furthermore, even if the liquid refrigerant flows out of the suction side evaporator 16 during the normal operation mode or the high-temperature refrigerant flowing into the suction side evaporator 16 condenses during the defrosting operation mode, the gas-liquid separator Since only the gas-phase refrigerant separated in 22 can be supplied to the second compressor 21, the problem of liquid compression of the second compressor 21 can be avoided.

  Of course, any of the first and second defrosting operation modes may be executed in the defrosting operation mode of the ejector refrigeration cycle 300 of the present embodiment.

(Twenty-ninth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 43, an example will be described in which the defrosting operation mode is realized by eliminating the bypass passage 25 and the on-off valve 26 with respect to the twenty-sixth embodiment. When the ejector refrigeration cycle 300 of the present embodiment is operated, the normal operation mode operates as shown in the Mollier diagram of FIG.

  The operation in the normal operation mode is the same as the operation in the normal operation mode of the twenty-sixth embodiment (FIG. 40A). On the other hand, in the defrosting operation mode, the control device operates the first and second electric motors 11b and 21b, the cooling fan 12a, and the blower fan 16a, and further, the throttle opening degree of the variable throttle mechanism 19 is set higher than that in the normal operation mode. increase.

  As a result, as shown in FIG. 44B, the refrigerant state in the defrosting operation mode changes in the same manner as in the normal operation mode, but the refrigerant evaporation pressure in the suction side evaporator 16 can be defrosted, that is, The refrigerant evaporation temperature can be raised to a temperature higher than 0 ° C.

  Therefore, in the defrosting operation mode of the present embodiment, the refrigerant evaporation temperature in the suction side evaporator 16 can be increased and the suction side evaporator 16 can be defrosted. Furthermore, in the normal operation mode, the same effect as that of the normal operation mode of the twenty-first embodiment can be obtained.

  Furthermore, if an electric expansion valve is employed instead of the temperature expansion valve 17 and the control device increases the throttle opening of the electric expansion valve in the defrosting operation mode, the outflow side evaporator The refrigerant evaporation temperature at 14 can also be increased.

(Thirty Embodiment)
An example in which the ejector refrigeration cycle 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. 45 is an overall configuration diagram of the ejector refrigeration cycle 400 of the present embodiment.

  The ejector refrigeration cycle 400 of the present embodiment is obtained by changing the components and the connection mode of the ejector refrigeration cycle 100 of the first embodiment, which is the premise thereof, that is, by changing the cycle configuration. is there. Therefore, in FIG. 45, the same or equivalent parts as those of the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  In the ejector refrigeration cycle 400, a first branch portion 18 that branches the flow of the high-pressure refrigerant that has flowed out of the radiator 12 is connected to the outlet side of the radiator 12. The 1st branch part 18 is comprised by the three-way coupling which has three inflow / outflow ports, and makes one refrigerant | coolant inflow port and two into a refrigerant | coolant outflow port.

  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. A temperature type expansion valve 17 as a high pressure side pressure reducing means is connected to one refrigerant outlet of the first branching portion 18, and a first variable throttle mechanism as a first suction side pressure reducing means is connected to the other refrigerant outlet. 19 side is connected.

  This temperature type expansion valve 17 has a temperature sensing part (not shown) arranged in an outlet side refrigerant passage on the outlet side evaporator 14 described later, and the temperature and pressure of the refrigerant on the outlet side of the outlet side evaporator 14. Based on this, the degree of superheat of the refrigerant on the outlet side of the outlet evaporator 14 is detected, and a variable throttle mechanism that adjusts the valve opening (refrigerant flow rate) by a mechanical mechanism so that this superheat degree becomes a predetermined value set in advance. It is.

  A nozzle portion 13 a of the ejector 13 is connected to the outlet side of the temperature type expansion valve 17. A refrigerant inflow port 28a of the second branch portion 28 is connected to the outlet side of the diffuser portion 13d of the ejector 13.

  The basic configuration of the second branch unit 28 is the same as that of the first branch unit 18. The outlet evaporator 14 is connected to one refrigerant outlet 28b of the second branch portion 28, and the second variable throttle mechanism 29 as a second suction side pressure reducing means is connected to the other refrigerant outlet 28c. Yes.

  Further, the second branch portion 28 of the present embodiment includes a flow direction of the refrigerant flowing out from the one refrigerant outlet 28b to the outlet-side evaporator 14 side, and a second variable throttle mechanism 29 side from the other refrigerant outlet 28c. The flow direction of the refrigerant flowing out of the diffuser portion 13d 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 28a from the diffuser portion 13d outlet side.

  Therefore, the refrigerant flowing into the second branch portion 28 flows out of the second branch portion 28 without unnecessarily reducing the flow velocity when the flow is branched. Thereby, the flow velocity (dynamic pressure) of the refrigerant flowing out from the ejector 15 in the second branch portion 28 is maintained. Of course, the 2nd branch part 28 is not limited to this, You may form in a substantially T shape.

  The outflow side evaporator 14 evaporates the low-pressure refrigerant and absorbs heat by exchanging heat between the refrigerant flowing out from one refrigerant outlet 28b of the second branch portion 28 and the air in the refrigerator circulated by the blower fan 14a. This is an endothermic heat exchanger that exerts its action. The suction port of the first compressor 11 is connected to the refrigerant outlet side of the outflow side evaporator 14.

  The second variable throttle mechanism 29 is for decompressing and expanding the refrigerant flowing out from the other refrigerant outlet 28 c of the second branch portion 28. The basic configuration of the first and second variable aperture mechanisms 19 and 29 is the same as that of the variable aperture mechanism 19 of the first embodiment. Therefore, when the second variable throttle mechanism 29 fully closes the throttle passage, the flow of the refrigerant flowing out from the diffuser portion 13d is not branched by the second branch portion 28, and the total flow rate is reduced to the outflow side evaporator 14. To the side.

  Further, as described above, the first variable throttle mechanism 19 is connected to the other refrigerant outlet of the first branch portion 18. Therefore, when the first variable throttle mechanism 19 fully closes the throttle passage, the flow of the refrigerant flowing out of the radiator 12 is not branched by the first branching portion 18, and the total flow rate is directed to the temperature type expansion valve 17 side. leak.

  The outlet side of the first and second variable throttle mechanisms 19 and 29 is connected to a merging section 20 that joins the refrigerant flows that have flowed out of the first and second variable throttle mechanisms 19 and 29. The basic configuration of the merging unit 20 is the same as that of the second branch unit 28. 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.

  Furthermore, in the junction part 20 of this embodiment, the flow direction of the refrigerant | coolant which flows in into the one refrigerant | coolant inlet 20b from the 1st variable throttle mechanism 19, and it flows in into the other refrigerant | coolant inlet 20c from the 2nd variable throttle mechanism 29. The flow direction of the refrigerant is substantially Y-shaped so as to face the target direction and intersect at an acute angle with respect to the flow direction of the refrigerant flowing out from the refrigerant outlet 20a to the suction side evaporator 16.

  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. As a result, the flow velocity (dynamic pressure) of the refrigerant flowing out from the first and second variable throttle mechanisms 19 and 29 is maintained in the merging portion 20.

  A suction-side evaporator 16 is connected to the refrigerant outlet 20 a of the junction 20. The suction port of the second compressor 21 is connected to the outlet side of the suction side evaporator 16, and the refrigerant suction port 13 b of the ejector 13 is connected to the discharge port of the second compressor 21.

  Further, in the ejector refrigeration cycle 400 of the present embodiment, similarly to the first embodiment, between the first compression mechanism 11a discharge port side and the radiator 12 inlet side, and the junction 20 outlet side and suction side. A bypass passage 25 is provided to connect the evaporator 16 to the inlet side. The bypass passage 25 is provided with an opening / closing valve 26 as an opening / closing means for opening / closing the bypass passage 25.

  The bypass passage 25 is provided so as to connect between the discharge side of the first compression mechanism 11a and the inlet side of the radiator 12, and between the outlet side of the first variable throttle mechanism 19 and the refrigerant inlet 20b side. Or it may be provided so as to connect between the discharge side of the first compression mechanism 11a and the inlet side of the radiator 12, and between the outlet side of the second variable throttle mechanism 29 and the refrigerant inlet 20c side. Good.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. 46 (a) is a Mollier diagram in the normal operation mode, and FIG. 46 (b) is a Mollier diagram in the defrosting operation mode.

  Here, in the ejector refrigeration cycle 400 of the present embodiment, the control device controls the first and second variable throttle mechanisms 19 and 29 to the throttle state or the fully closed state in the normal operation mode, so that the following 3 Different types of cycle configurations can be realized.

  When the control device sets the first variable throttling mechanism 19 to the fully closed state and the second variable throttling mechanism 29 to the throttling state, it is possible to realize a cycle configuration in which the refrigerant flow is branched only by the second branch portion 28 (hereinafter, referred to as “the second variable throttling mechanism 28”). The operation mode in this cycle configuration is called the low pressure branch operation mode).

  When the control device places the first variable throttling mechanism 19 in the throttling state and the second variable throttling mechanism 29 in the fully closed state, it is possible to realize a cycle configuration in which the refrigerant flow is branched only by the first branching section 18 (hereinafter, referred to as “the first variable throttling mechanism 29”). The operation mode in this cycle configuration is called a high-pressure branch operation mode).

  When the control device places both the first and second variable throttle mechanisms 19 and 29 in the throttle state, it is possible to realize a cycle configuration in which the refrigerant flow is branched at the first branch portion 18 and the second branch portion 28 at the same time (hereinafter, The operation mode in this cycle configuration is called the simultaneous branch operation mode).

  Moreover, each operation mode in said normal 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.

First, the normal operation mode will be described with reference to FIG. In the low-pressure branch operation mode of the normal operation mode, the high-temperature and high-pressure gas-phase refrigerant (a ₄₆ points) discharged from the first compressor 11 flows into the radiator 12 and blown air blown from the cooling fan 12a ( Heat exchanges with the outside air to dissipate heat and condense (a ₄₆ points → b ₄₆ points). The refrigerant that has flowed out of the radiator 12 flows into the first branch portion 18.

At this time, since the first variable throttle mechanism 19 is in a fully closed state, the flow of the refrigerant flowing out of the radiator 12 is not branched in the first branch portion 18, and the total flow rate thereof is the temperature type expansion valve 17. Flow into. The refrigerant that has flowed into the temperature type expansion valve 17 expands under reduced pressure in an iso-enthalpy manner and enters a gas-liquid two-phase state (b ₄₆ points → c ₄₆ points). At this time, the valve opening degree of the temperature type expansion valve 17 is adjusted such that the degree of superheat (g ₄₆ points) of the outlet side refrigerant 14 outlet side refrigerant becomes a predetermined value.

The intermediate-pressure refrigerant flowing out of the thermal expansion valve 17, flows into the nozzle portion 13a of the ejector 13, isentropically decompressed to expand (c ₄₆ points → d ₄₆ points). And the pressure energy of a refrigerant | coolant is converted into speed energy at the time of this decompression | expansion expansion, and a refrigerant | coolant is injected at high speed from the refrigerant | coolant injection port of the nozzle part 13a. Due to the refrigerant suction action of the injected refrigerant, the refrigerant discharged from the second compressor 21 is sucked from the refrigerant suction port 13b (j ₄₆ points → e ₄₆ points).

Furthermore, the suction refrigerant sucked from the injection refrigerant and the refrigerant suction port 13b that is injected from the nozzle portion 13a are mixed in the mixing section 13c of the ejector 13, and flows into the diffuser portion 13d (d ₄₆ points → e ₄₆ points). In the diffuser portion 13d, the passage energy is increased and the velocity energy of the refrigerant is converted into pressure energy, so that the pressure of the refrigerant rises (e ₄₆ points → f ₄₆ points).

  The refrigerant that has flowed out of the diffuser portion 13d is branched into a refrigerant flow that flows into the outflow-side evaporator 14 side and a refrigerant flow that flows into the second variable throttle mechanism 29 side at the second branch portion 28. At this time, the control device increases the refrigerant flow rate G1 flowing into the outflow side evaporator 14 side more than the refrigerant flow rate G2 flowing into the second variable throttle mechanism 29 side, and the refrigerant evaporation temperature in the suction side evaporator 16 is set in advance. The throttle opening of the second variable throttle mechanism 29 is adjusted so that the predetermined temperature is set.

The refrigerant flowing into the outflow side evaporator 14 from the second branch portion 28 absorbs heat from the air in the refrigerator circulated and blown by the blower fan 14a and evaporates (f ₄₆ points → g ₄₆ points). Thereby, the air in a refrigerator is cooled. Then, the refrigerant flowing out of the outflow side evaporator 14 is sucked into the first compressor 11 and compressed again (g ₄₆ point → a ₄₆ point).

On the other hand, the refrigerant that has flowed into the second variable throttle mechanism 29 from the second branch portion 28 is further decompressed and expanded in an enthalpy manner to reduce its pressure (f ₄₆ point → hα ₄₆ point). The refrigerant expanded under reduced pressure by the second variable throttle mechanism 29 flows into the suction side evaporator 16, absorbs heat from the air in the freezer circulated by the blower fan 16a, and evaporates (hα ₄₆ points → i ₄₆ points). ). Thereby, the air in a freezer is cooled.

Then, the refrigerant flowing out from the suction side evaporator 16 is sucked into the second compressor 21 and compressed (i ₄₆ points → j ₄₆ points). At this time, the control device controls the operations of the first and second electric motors 11b and 21b so that the COP of the ejector refrigeration cycle as a whole approaches a maximum.

Further, as described above, the refrigerant discharged from the second compressor 21 is sucked into the ejector 13 from the refrigerant suction port 13b (j ₄₆ points → e ₄₆ points).

In the high-pressure branch operation mode in the normal operation mode, the refrigerant discharged from the first compressor 11 dissipates heat in the radiator 12 and condenses (a ₄₆ points → b ₄₆ points) as in the low-pressure branch operation mode. The refrigerant that has flowed out of the radiator 12 is branched at the first branch portion 18.

The high-pressure refrigerant that has flowed into the temperature-type expansion valve 17 from the first branch portion 18 is decompressed and expanded in an enthalpy manner at the temperature-type expansion valve 17 in the same manner as in the low-pressure branch operation mode, and enters a gas-liquid two-phase state (b) ₄₆ points → c ₄₆ points). Further, the intermediate pressure refrigerant flowing out of the temperature type expansion valve 17 flows in the order of the nozzle portion 13a of the ejector 13 → the diffuser portion 13d → the second branch portion 28 → the outflow side evaporator 14 (c ₄₆ points → d ₄₆ points → e ₄₆ points → f ₄₆ points).

In this operation mode, since the second variable throttle mechanism 29 is in a fully closed state, the flow of the refrigerant flowing out from the diffuser portion 13d is not branched in the second branching portion 28, and the entire flow rate is evaporated on the outflow side. Flows into the vessel 14. The refrigerant flowing into the outflow side evaporator 14 from the second branch portion 28 absorbs heat from the air in the refrigerator and evaporates (f ₄₆ point → g ₄₆ point), as in the low pressure branch operation mode, and enters the first compressor 11. Inhaled and compressed again (g ₄₆ points → a ₄₆ points).

On the other hand, the high-pressure refrigerant that has flowed into the first variable throttle mechanism 19 from the first branch portion 18 is decompressed and expanded in an enthalpy manner by the first variable throttle mechanism 19 as shown by the broken line in FIG. The pressure is reduced (b ₄₆ points → hβ ₄₆ points).

  At this time, the valve opening degree (throttle opening degree) of the first variable throttle mechanism 19 is such that the flow rate ratio Ge / Gnoz between the refrigerant flow rate Gnoz flowing into the nozzle portion 13a side and the refrigerant flow rate Ge flowing into the refrigerant suction port 13b side. The flow rate is adjusted so as to obtain an optimum flow rate ratio capable of exhibiting a high COP as a whole cycle. The refrigerant decompressed and expanded by the first variable throttle mechanism 19 flows into the junction 20.

As shown by the broken line in FIG. 46A, the refrigerant flowing into the suction-side evaporator 16 from the junction 20 absorbs heat from the air in the freezer circulated by the blower fan 16a and evaporates (hβ ₄₆ points → i ₄₆ points). Thereby, the air in a freezer is cooled. Further, the refrigerant that has flowed out of the suction-side evaporator 16 is compressed by the second compressor 21 (i ₄₆ points → j ₄₆ points) in the same manner as in the low pressure branch operation mode, and is sucked into the refrigerant suction port 13b of the ejector 13. (J ₄₆ points → e ₄₆ points).

Among the normal operation modes, in the simultaneous branch operation mode, the refrigerant that has flowed out of the radiator 12 is branched at the first branch portion 18 as in the high-pressure branch operation mode. The refrigerant flowing out from the first branch portion 18 toward the temperature type expansion valve 17 flows in the order of the temperature type expansion valve 17 → the nozzle portion 13a of the ejector 13 → the diffuser portion 13d → the second branch portion 28 (b ₄₆ → c ₄₆ points → d ₄₆ points → e ₄₆ points → f ₄₆ points).

Moreover, in the 2nd branch part 28, the flow of the refrigerant | coolant which flowed out from the diffuser part 13d is branched like the low voltage | pressure branch operation mode. The refrigerant flowing out from the second branch portion 28 to the outflow side evaporator 14 flows in the order of the outflow side evaporator 14 → the first compressor 11 to cool the refrigerator air (f ₄₆ points → g ₄₆ points). .

Furthermore, the refrigerant that has flowed out from the second branch portion 28 to the second variable throttle mechanism 29 side flows in the order of the second variable throttle mechanism 29 → the merging portion 20 (c ₄₆ points → hβ ₄₆ points). The refrigerant flowing from the first branch portion 18 to the first variable throttle mechanism 19 side flows in the order of the first variable throttle mechanism 19 → merging portion 20 (f ₄₆ points → h [alpha ₄₆ points).

Then, as shown by a thin line in FIG. 46A, the flow of the refrigerant that has flowed out of the second variable throttle mechanism 29 and the flow of the refrigerant that has flowed out of the first variable throttle mechanism 19 are merged at the merging portion 20 ( hβ ₄₆ points → hγ ₄₆ points, hα ₄₆ points → hγ ₄₆ points). The refrigerant that has flowed out from the merging portion 20 flows into the suction-side evaporator 16 and evaporates, similarly to the low-pressure branch operation mode and the high-pressure branch operation mode, to cool the freezer air.

The refrigerant flowing out of the suction side evaporator 16 is compressed by the second compressor 21 and sucked into the refrigerant suction port 13b of the ejector 13 (hγ ₄₆ points → i ₄₆ points → j ₄₆ points → e ₄₆ points). .

  Next, the defrosting operation mode will be described. The defrosting operation mode is executed when the changeover switch is switched to the defrosting operation mode in a state where the operation switch of the operation panel is turned on. In the ejector refrigeration cycle 400 of this embodiment, two types of defrosting operation modes can be executed. In the defrosting operation mode of this embodiment, among these two types of defrosting operation modes, the first defrosting operation mode is operated. The second defrosting operation mode will be described later.

When the defrosting operation mode is executed, the control device operates the first and second electric motors 11b and 21b. As a result, the first compressor 11 sucks the refrigerant, compresses it, and discharges it ( _k46 point in FIG. 46B). Further, the control device fully opens the throttle openings of the first and second variable throttle mechanisms 19 and 29, opens the on-off valve 26, and stops the cooling fan 12a and the blower fans 14a and 16a.

Since the on-off valve 26 is in the open state, the high-temperature and high-pressure gas-phase refrigerant discharged from the first compressor 11 flows into the bypass passage 25 and passes through the on-off valve 26. It expands under reduced pressure enthalpy (k ₄₆ points → l ₄₆ points).

  The high-temperature and low-pressure gas-phase refrigerant that has passed through the on-off valve 26 has the throttle opening of the first variable throttle mechanism 19 fully closed, so that the first branching section 18 side via the first variable throttle mechanism 19 It does not flow into. Furthermore, since the throttle opening of the second variable throttle mechanism 29 is in a fully closed state, the second variable throttle mechanism 29 does not flow into the second branch portion 28 side. That is, the entire flow rate of the high-temperature and low-pressure gas-phase refrigerant that has passed through the on-off valve 26 flows into the suction-side evaporator 16.

The refrigerant flowing into the suction-side evaporator 16 dissipates the amount of heat to the suction-side evaporator 16 (l ₄₆ points → m ₄₆ points). As a result, the suction side evaporator 16 is defrosted. The refrigerant radiated by the suction side evaporator 16 is sucked into the second compressor 21 and compressed (m ₄₆ points → n ₄₆ points).

The refrigerant discharged from the second compressor 21 is depressurized due to the pressure loss when passing through the refrigerant suction port 13b → the mixing part 13c → the diffuser part 13d of the ejector and flows into the outflow side evaporator 14 (n ₄₆ points). → o ₄₆ points).

The refrigerant that has flowed into the outflow side evaporator 14 dissipates the amount of heat to the outflow side evaporator 14 (from o ₄₆ point to p ₄₆ point). Thereby, the defrosting of the outflow side evaporator 14 is made. The refrigerant radiated by the outflow side evaporator 14 is sucked into the first compressor 11 and compressed again (p ₄₆ points → k ₄₆ points).

  Since the ejector refrigeration cycle 400 of this embodiment operates as described above, the following effects can be exhibited.

  (A) In any operation mode at the time of the normal operation mode, the flow of the refrigerant is divided in at least one of the first branch part 18 and the second branch part 28, so the outflow side evaporator 14 and the suction side evaporator The refrigerant can be appropriately supplied to both 16. Therefore, both the outflow side evaporator 14 and the suction side evaporator 16 can exhibit a cooling action simultaneously.

  At this time, the refrigerant evaporation pressure of the suction side evaporator 16 becomes the pressure after the pressure is increased by the diffuser portion 13 d and then further reduced by the variable throttle mechanism 19, and the refrigerant evaporation pressure of the outflow side evaporator 14 is the pressure of the suction side evaporator 16. The refrigerant evaporation pressure becomes the pressure after being increased by the second compressor 21 and the diffuser unit 13d.

  Therefore, the refrigerant evaporation pressure (refrigerant evaporation temperature) of the suction side evaporator 16 can be made sufficiently lower than the refrigerant evaporation pressure (refrigerant evaporation temperature) of the outflow side evaporator 14. As a result, the outflow evaporator 14 can be used for cooling in a low-temperature refrigerator, and the suction-side evaporator 16 can be used for cooling in a cryogenic freezer.

  (B) In any of the operation modes during the normal operation mode, even if the operation condition is such that the drive flow of the ejector 13 decreases, that is, the operation condition such that the suction capacity of the ejector 13 decreases, the second By the action of the compressor 21 (second compression mechanism 21a), the ejector refrigeration cycle 400 as a whole can be stably operated in a state where a high COP is exhibited, as in the first embodiment.

  (C) In the low-pressure branch operation mode in the normal operation mode, the refrigerant flow rate G1 flowing from the second branch portion 28 to the outflow side evaporator 14 side flows from the second branch portion 28 to the second temperature expansion valve 29 side. Since the refrigerant flow rate G2 is larger than the refrigerant flow rate G2, a larger amount of refrigerant can be radiated 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.

  (D) In the high-pressure branch operation mode and the simultaneous branch operation mode in the normal operation mode, the first compressor 11 → the radiator 12 → the first branch part 18 → the ejector 13 → the second branch part 28 → the outflow side evaporator 14 → The refrigerant flows in the order of the first compressor 11, and further, the first compressor 11 → the radiator 12 → the first branching portion 18 → the first variable throttle mechanism 19 → the merging portion 20 → the suction side evaporator 16 → the second compressor. The refrigerant flows in the order of 11 → the ejector 13 → the second branch portion 28 → the outflow side evaporator 14 → the first compressor 11.

  That is, since the flow of the refrigerant passing through the evaporator such as the outflow side evaporator 14 and the suction side evaporator 16 is annular, lubricating oil (refrigerator oil) for the first and second compressors 11 and 21 is used as the refrigerant. Even if mixed, it is possible to prevent the oil from staying in the outflow side evaporator 14 and the suction side evaporator 16.

  (E) In the simultaneous branch operation mode in the normal operation mode, a cycle configuration in which the refrigerant flowing out from both the first variable throttle mechanism 19 and the second variable throttle mechanism 29 is supplied to the suction side evaporator 16 can be realized. Accordingly, the refrigerant supplied to the suction side evaporator 16 with respect to the cycle configuration in which the refrigerant flowing out from either the first variable throttle mechanism 19 or the second variable throttle mechanism 29 is supplied to the suction side evaporator 16. It becomes easy to increase the flow rate.

  (F) Since the temperature type expansion valve 17 which is a variable throttle mechanism is employed as the high pressure side pressure reducing means in the normal operation mode, the flow rate of the refrigerant flowing into the nozzle portion 13a of the ejector 13 is changed according to the cycle load fluctuation. Can be changed. As a result, the ejector-type refrigeration cycle can be operated while exhibiting a high COP even if load fluctuation occurs.

(G) to the normal operation mode, since the reduced pressure expanded refrigerant at a temperature expansion valve 17 (c ₂ points in FIG. 46) is a gas-liquid two-phase state, gas-liquid two-phase state to the nozzle portion 13a of the ejector 13 The refrigerant can be introduced. Therefore, the boiling of the refrigerant in the nozzle portion 13a can be promoted and the nozzle efficiency can be improved as compared with the case where the liquid phase refrigerant is caused to flow into the nozzle portion 13a.

  Accordingly, the amount of recovered energy can be increased and the amount of pressure increase in the diffuser section 13d can be increased, so that the COP can be further improved. Furthermore, since the refrigerant passage area of the nozzle part 13a can be enlarged with respect to the case where the liquid phase refrigerant is caused to flow into the nozzle part 13a, the processing of the nozzle part 13a is facilitated. As a result, the manufacturing cost of the ejector 13 can be reduced, and the manufacturing cost of the ejector refrigeration cycle 10 as a whole can be reduced.

  Further, when frost formation occurs in the outflow side evaporator 14 and the suction side evaporator 16, the control device opens the on-off valve 26 so that the high-temperature refrigerant discharged from the first compressor 11 is removed from the suction side evaporator. It is possible to execute a defrosting operation mode in which the defrosting is performed by flowing into the refrigerant 16 and the high-temperature refrigerant discharged from the second compressor 21 is caused to flow into the outflow evaporator 14 to defrost.

  Therefore, it is possible to stably operate the ejector-type refrigeration cycle 400 while avoiding cycle failure due to frost formation on the outflow side evaporator 14 and the suction side evaporator 16. Further, the first and second variable throttle mechanisms 19 and 29 are employed as the pressure reducing means, and the throttle openings of the first and second variable throttle mechanisms 19 and 29 are fully closed during the defrosting operation. It is possible to reliably prevent the refrigerant flowing out from the refrigerant from flowing to the branching portion 18 side through the first and second variable throttle mechanisms 19 and 29.

  Here, defrosting in the second defrosting operation mode among the two types of defrosting operation modes described above will be described with reference to FIG. FIG. 46C is a Mollier diagram in the second defrosting operation mode.

  When the second defrosting operation mode is executed, similarly to the first defrosting operation mode, the control device operates the first and second electric motors 11b and 21b to open the on-off valve 26, and the cooling fan 12a and the blower fans 14a and 16a are stopped. Further, the control device sets the throttle opening of the first variable throttle mechanism 19 to a fully open state and sets the throttle opening of the second variable throttle mechanism 29 to a fully open state.

In the second defrosting operation mode, the first variable throttle mechanism 19 is fully open and the second variable throttle mechanism 29 is fully open, so that the flow of the refrigerant flowing out from the bypass passage 25 (1 ′ ₄₆ points) flows. The refrigerant flow is divided into a refrigerant flow flowing toward the suction side evaporator 16 and a refrigerant flow flowing toward the second variable throttle mechanism 29 side.

The high-temperature and low-pressure gas-phase refrigerant that has flowed out of the on-off valve 26 toward the suction-side evaporator 16 releases heat to the suction-side evaporator 16 (1 ′ ₄₆ points → m ′ ₄₆ points). As a result, the suction side evaporator 16 is defrosted. The refrigerant that has dissipated heat in the suction side evaporator 16 is sucked into the second compressor 21 and compressed (m ′ ₄₆ points → n ′ ₄₆ points).

The refrigerant discharged from the second compressor 21 is depressurized by pressure loss when passing through the refrigerant suction port 13b → mixing part 13c → diffuser part 13d of the ejector (n ′ ₄₆ points → o ′ ₄₆ points). Further, the refrigerant that has flowed out of the diffuser portion 13d merges with the refrigerant that has flowed out of the second variable throttle mechanism 29 and flows into the outflow side evaporator 14 (n ′ ₄₆ points → o ″ ₄₆ points, l ′ ₄₆ points → o ” ₄₆ points).

The refrigerant flowing into the outflow side evaporator 14 dissipates the amount of heat to the outflow side evaporator 14 (o ″ ₄₆ points → p ′ ₄₆ points), whereby the outflow side evaporator 14 is defrosted. The refrigerant that has dissipated heat in the side evaporator 14 is sucked into the first compressor 11 and compressed again (p ′ ₄₆ points → k ′ ₄₆ points).

  According to the second defrosting operation mode, not only the outflow side evaporator 14 and the suction side evaporator 16 can be defrosted as in the first defrosting operation mode, but also the pressure of the refrigerant flowing into the outflow side evaporator 14 is reduced. It can also be lowered to protect the outflow side evaporator 14.

  That is, in this embodiment, the pressure of the refrigerant flowing into the outflow side evaporator 14 can be reduced by joining the refrigerant flowing out from the diffuser portion 13d with the refrigerant flowing out from the second variable throttle mechanism 29.

  Therefore, it is possible to effectively prevent the refrigerant pressure in the outflow side evaporator 14 from exceeding the pressure resistance performance in the outflow side evaporator 14 and to protect the outflow side evaporator 14. Further, as described above, since the refrigerant pressure in the outflow side evaporator 14 can be reduced, the refrigerant pressure (refrigerant temperature) in the suction side evaporator 16 is increased within the allowable pressure resistance of the suction side evaporator 16. You may let them.

(Thirty-first embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 47, an example in which the connection mode of the bypass passage 25 is changed with respect to the 30th embodiment will be described.

  Specifically, the bypass passage 25 of the present embodiment is between the radiator 12 outlet side and the first branch portion 18 inlet side, and between the junction portion 20 outlet side and the suction side evaporator 16 inlet side. It is provided to connect. Therefore, the bypass passage 25 constitutes a refrigerant flow path that guides the high-pressure refrigerant of the cycle downstream of the radiator 12 to the suction-side evaporator 16.

  When the ejector refrigeration cycle 400 of the present embodiment is operated, the normal operation mode operates in the same manner as the Mollier diagram of FIG. 46 (a) of the 30th embodiment. On the other hand, in the defrosting operation mode, since the control device stops the cooling fan 12 a, the refrigerant discharged from the first compressor 11 does not radiate heat at the radiator 12. For this reason, also in the defrosting operation mode, it operates similarly to the Mollier diagram of FIG. 46B of the 26th embodiment.

  Therefore, also in this embodiment, the same effect as that in the thirtieth embodiment can be obtained. Of course, any of the first and second defrosting operation modes may be executed in the defrosting operation mode of the ejector refrigeration cycle 400 of the present embodiment.

(Thirty-second embodiment)
In the present embodiment, an example in which a gas-liquid separator 22 is added to the thirtieth embodiment will be described as shown in the overall configuration diagram of FIG. The gas-liquid separator 22 is a suction-side gas-liquid separator that separates the gas-liquid refrigerant flowing out from the suction-side evaporator 16 and accumulates excess refrigerant in the cycle.

  When the ejector refrigeration cycle 400 of this embodiment is operated, it operates similarly to the Mollier diagram of FIG. 46 of the 30th embodiment both in the normal operation mode and in the defrosting operation mode. Therefore, the same effect as that of the thirtieth embodiment can be obtained.

  Furthermore, even if the liquid refrigerant flows out of the suction side evaporator 16 during the normal operation mode or the high-temperature refrigerant flowing into the suction side evaporator 16 condenses during the defrosting operation mode, the gas-liquid separator Since only the gas-phase refrigerant separated in 22 can be supplied to the second compressor 21, the problem of liquid compression of the second compressor 21 can be avoided.

(Thirty-third embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 49, an example will be described in which the defrosting operation mode is realized by eliminating the bypass passage 25 and the on-off valve 26 with respect to the thirtieth embodiment. When the ejector refrigeration cycle 400 of the present embodiment is operated, the normal operation mode operates as shown in the Mollier diagram of FIG.

  The operation in the normal operation mode is the same as the operation in the normal operation mode of the thirtieth embodiment (FIG. 46 (a)). In addition, the code | symbol which shows the state of the refrigerant | coolant in FIG. 50 uses the same code | symbol as the code | symbol which shows the state of the same refrigerant | coolant in FIG. 46, and has changed only the subscript.

  On the other hand, in the defrosting operation mode, the control device operates the first and second electric motors 11b and 21b, the cooling fan 12a, and the blower fan 16a, and further, the throttle opening degree of the first and second variable throttle mechanisms 19 and 29. Is increased from that in the normal operation mode. In order to defrost the suction side evaporator 16 having a low refrigerant evaporation temperature, the throttle opening degree of at least one of the first and second variable throttle mechanisms 19 and 29 may be increased.

  As a result, as shown in FIG. 50B, the refrigerant state in the defrosting operation mode changes in the same manner as in the normal operation mode, but the refrigerant evaporation pressure in the suction side evaporator 14 and the suction side evaporator 16 is removed. It is possible to frost, that is, the refrigerant evaporation temperature can be raised to a temperature higher than 0 ° C.

  Therefore, in the defrosting operation mode of the present embodiment, the refrigerant evaporating temperature in the outflow side evaporator 14 and the suction side evaporator 16 is raised to defrost the outflow side evaporator 14 and the suction side evaporator 16. it can. Furthermore, in the normal operation mode, the same effects as in the normal operation mode of the thirtieth embodiment can be obtained.

(Thirty-fourth embodiment)
An example in which the ejector refrigeration cycle 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. 51 is an overall configuration diagram of an ejector refrigeration cycle 500 of the present embodiment.

  The ejector refrigeration cycle 500 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 FIG. 51, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  In the ejector refrigeration cycle 500, as shown in the overall configuration diagram of FIG. 51, the branch portion 38 is disposed on the discharge port side of the first compressor 11. The branch portion 38 is configured by a three-way joint having three inflow / outflow ports, and 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. A first radiator 121 is connected to one refrigerant outlet of the branch portion 38, and a 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 38 and the outside air (outside air) blown by the cooling fan 121a, and dissipates the high-pressure refrigerant to cool it. It is a heat exchanger for heat dissipation. The first radiator 122 heat-exchanges the high-pressure refrigerant flowing out from the other refrigerant outlet of the branch portion 38 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 ejector refrigeration cycle 500 of the present embodiment, the heat exchange capacity (heat radiation performance) of the first radiator 121 is reduced by reducing the heat exchange area of the first radiator 121 relative to the second radiator. The heat exchange capacity of the second radiator 122 is lowered. 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.

  Also, a receiver (receiver) as a high-pressure side gas-liquid separator that separates the gas-liquid refrigerant flowing out of the second radiator 122 and stores excess liquid-phase refrigerant at the outlet side of the second radiator 122. May be provided. Then, the saturated liquid phase refrigerant separated from the receiver may be led to the downstream side.

  On the outlet side of the first radiator 121, a temperature type expansion valve 17 is connected as high pressure side pressure reducing means similar to that of the first embodiment. Furthermore, the outlet side of the temperature type expansion valve 17 is connected to the inlet side of the nozzle portion 13a of the ejector 13 similar to that of the first embodiment. Further, an outlet-side evaporator 14 is connected to the outlet side of the diffuser portion 13d of the ejector 13.

  On the other hand, the suction side evaporator 16 is connected to the outlet side of the second radiator 122 via a variable throttle mechanism 19 as suction side pressure reducing means. The suction port of the second compressor 21 is connected to the outlet side of the suction side evaporator 16, and the refrigerant suction port 13 b of the ejector 13 is connected to the discharge port of the second compressor 21.

  Further, in the ejector refrigeration cycle 500 of the present embodiment, similarly to the first embodiment, the suction between the discharge side of the first compression mechanism 11a and the inlet side of the branch portion 38, the outlet side of the variable throttle mechanism 19 and the suction side. A bypass passage 25 for connecting the side evaporator 16 to the inlet side is provided. The bypass passage 25 is provided with an opening / closing valve 26 as an opening / closing means for opening / closing the bypass passage 25.

  Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. Fig. 52 (a) is a Mollier diagram in the normal operation mode, and Fig. 52 (b) is a Mollier diagram in the defrosting operation mode. First, the normal operation mode will be described. The normal operation mode is executed when the operation switch of the operation panel is turned on and the changeover switch is switched to the normal operation mode.

When the normal operation mode is executed, the control device operates the first and second electric motors 11b and 21b, the first and second cooling fans 121a and 122a, and the blower fans 14a and 16a. Thereby, the 1st compressor 11 suck | inhales a refrigerant | coolant, compresses and discharges ( _a52 point of Fig.52 (a)). Further, the control device adjusts the throttle opening degree of the variable throttle mechanism 19 so that the refrigerant evaporation temperature in the suction side evaporator 16 becomes a predetermined temperature, and the on-off valve 26 is closed.

  The high-temperature and high-pressure gas-phase refrigerant discharged from the first compressor 11 flows into the branch portion 38 and is divided into a refrigerant flow flowing into the first radiator 121 side and a refrigerant flow flowing into the second radiator 122 side. Is done.

  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 38 are determined so as to obtain the optimum flow rate ratio.

The refrigerant flowing into the first radiator 121 side exchanges heat with the blown air (outside air) blown from the cooling fan 121a to dissipate heat and condense (a point ₅₂ → b1 ₅₂ point). The refrigerant having flowed into the second radiator 122 side, the cooling blower has been blown air from the fan 122a (outside air) and heat exchanger to be condensed heat radiation (a ₅₂ point → b2 ₅₂ 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 higher than the enthalpy of the refrigerant that has flowed out.

The refrigerant flowing out of the first radiator 121 flows into the temperature type expansion valve 17 and is decompressed and expanded in an enthalpy manner to be in a gas-liquid two-phase state (b1 ₅₂ point → c ₅₂ point). At this time, the opening degree of the temperature type expansion valve 17 is adjusted so that the degree of superheat (g ₅₂ points) of the outlet side refrigerant 14 outlet side refrigerant becomes a predetermined value.

The intermediate-pressure refrigerant flowing out of the thermal expansion valve 17 isentropically depressurized expanded in the nozzle portion 13a (c ₅₂ points → d ₅₂ points). Then, the suction refrigerant sucked from injected injected refrigerant and the refrigerant suction port 13b of the nozzle portion 13a is mixed in the mixing portion 13c of the ejector 13 (d ₅₂ points → e ₅₂ points, j ₅₂ points → e ₅₂ points ), The pressure is increased by the diffuser section 13d (e ₅₂ points → f ₅₂ points).

Refrigerant flowing out of the diffuser unit 13d, and flows into the discharge side evaporator 14, and absorbs heat from the circulation blower has been refrigerator air by the blower fan 14a to evaporate (f ₅₂ points → g ₅₂ points). Thereby, the air in a refrigerator is cooled. Then, the refrigerant flowing out of the outflow side evaporator 14 is sucked into the first compressor 11 and compressed again (g ₅₂ points → a ₅₂ points).

The refrigerant flowing out of the second radiator 122, the variable throttle is isenthalpic depressurize expansion further by mechanism 19, reduces the pressure (b2 ₅₂ points → h ₅₂ points). Variable decompressed and expanded refrigerant in the diaphragm mechanism 19, and flows into the suction side evaporator 16, the blower fan 16a is evaporated by absorbing heat from the freezer in air circulated blown (h ₅₂ points → i ₅₂ points). Thereby, the air in a warehouse is cooled.

The refrigerant flowing out of the suction side evaporator 16 is sucked into the second compressor 21 and compressed (i ₅₂ points → j ₅₂ points). At this time, the control device controls the operations of the first and second electric motors 11b and 21b in the same manner as in the first embodiment so that the COP of the ejector refrigeration cycle 200 as a whole approaches the maximum.

Further, as described above, the refrigerant discharged from the second compressor 21 is sucked into the ejector 13 from the refrigerant suction port 13b (j ₅₂ points → e ₅₂ points).

  Next, the defrosting operation mode will be described. The defrosting operation mode is executed when the changeover switch is switched to the defrosting operation mode in a state where the operation switch of the operation panel is turned on.

When the defrosting operation mode is executed, the control device operates the first and second electric motors 11b and 21b. Thereby, the 1st compressor 11 suck | inhales a refrigerant | coolant, compresses and discharges. State of the refrigerant at this time is k ₅₂ points in FIG. 52 (b). Furthermore, the control device sets the throttle opening of the variable throttle mechanism 19 to a fully closed state, opens the on-off valve 26, and stops the first and second cooling fans 121a and 122a and the blower fans 14a and 16a.

Since the on-off valve 26 is in the open state, the high-temperature and high-pressure gas-phase refrigerant discharged from the first compressor 11 flows into the bypass passage 25 and passes through the on-off valve 26. It expands under reduced pressure enthalpy (k ₅₂ points → l ₅₂ points).

  The high-temperature and low-pressure gas-phase refrigerant that has passed through the on-off valve 26 has the throttle opening degree of the variable throttle mechanism 19 fully closed, and therefore the first and second radiators 121 and 122 via the variable throttle mechanism 19. It flows into the suction side evaporator 16 without flowing into the side.

The refrigerant that has flowed into the suction-side evaporator 16 dissipates the amount of heat to the suction-side evaporator 16 (l ₅₂ points → m ₅₂ points). As a result, the suction side evaporator 16 is defrosted. The refrigerant radiated by the suction-side evaporator 16 is sucked into the second compressor 21 and compressed (m ₅₂ points → n ₅₂ points).

The refrigerant discharged from the second compressor 21 is depressurized by the pressure loss when passing through the refrigerant suction port 13b → the mixing part 13c → the diffuser part 13d of the ejector and flows into the outflow evaporator 14 (n ₅₂ points). → o ₅₂ points).

The refrigerant flowing into the outflow side evaporator 14 dissipates the amount of heat to the outflow side evaporator 14 (o ₅₂ point → p ₅₂ point). Thereby, the defrosting of the outflow side evaporator 14 is made. The refrigerant having released heat in the discharge side evaporator 14 is compressed again is sucked into the first compressor 11 (p ₅₂ points → k ₅₂ points).

  Since the ejector refrigeration cycle 500 according to this embodiment operates as described above, the following effects can be exhibited.

  (A) In the normal operation mode, the flow of the refrigerant is divided by the branch portion 38, so that the refrigerant can be appropriately supplied to both the outflow side evaporator 14 and the suction side evaporator 16. Therefore, both the outflow side evaporator 14 and the suction side evaporator 16 can exhibit a cooling action simultaneously.

  At this time, the refrigerant evaporation pressure of the suction side evaporator 16 becomes the pressure after the pressure is increased by the diffuser portion 13 d and then further reduced by the variable throttle mechanism 19, and the refrigerant evaporation pressure of the outflow side evaporator 14 is the pressure of the suction side evaporator 16. The refrigerant evaporation pressure becomes the pressure after being increased by the second compressor 21 and the diffuser unit 13d.

  Therefore, the refrigerant evaporation pressure (refrigerant evaporation temperature) of the suction side evaporator 16 can be made sufficiently lower than the refrigerant evaporation pressure (refrigerant evaporation temperature) of the outflow side evaporator 14. As a result, the outflow evaporator 14 can be used for cooling in a low-temperature refrigerator, and the suction-side evaporator 16 can be used for cooling in a cryogenic freezer.

  (B) In the normal operation mode, the second compressor 21 (second compression) even if the operation condition is such that the drive flow of the ejector 13 decreases, that is, the suction condition of the ejector 13 decreases. By the action of the mechanism 21a), as in the first embodiment, the ejector refrigeration cycle 500 as a whole can be stably operated in a state where a high COP is exhibited.

  (C) In the normal operation mode, the refrigerant flows in the order of the first compressor 11 → the branching section 38 → the first radiator 121 → the temperature expansion valve 17 → the ejector 13 → the outflow side evaporator 14 → the first compressor 11. Further, the first compressor 11 → the branching section 38 → the second radiator 122 → the variable throttle mechanism 19 → the suction side evaporator 16 → the second compressor 11 → the ejector 13 → the outflow side evaporator 14 → the first compressor 11 The refrigerant flows in order.

  That is, since the flow of the refrigerant passing through the evaporator such as the outflow side evaporator 14 and the suction side evaporator 16 is annular, lubricating oil (refrigerator oil) for the first and second compressors 11 and 21 is used as the refrigerant. Even if mixed, it is possible to prevent the oil from staying in the outflow side evaporator 14 and the suction side evaporator 16.

  (D) In the normal operation mode, the temperature type expansion valve 17 which is a variable throttle mechanism is employed as the high pressure side pressure reducing means, so that the flow rate of the refrigerant flowing into the nozzle portion 13a of the ejector 13 is changed according to the cycle load fluctuation Can be changed. As a result, the ejector-type refrigeration cycle can be operated while exhibiting a high COP even if load fluctuation occurs.

(E) to the normal operation mode, refrigerant reduced in pressure by the thermal expansion valve 17 (c ₅₂ points in FIG. 52) because the gas-liquid two-phase state, a gas-liquid two-phase state to the nozzle portion 13a of the ejector 13 A refrigerant can be introduced. Therefore, the boiling of the refrigerant in the nozzle portion 13a can be promoted and the nozzle efficiency can be improved as compared with the case where the liquid phase refrigerant is caused to flow into the nozzle portion 13a.

  Accordingly, the amount of recovered energy can be increased and the amount of pressure increase in the diffuser section 13d can be increased, so that the COP can be further improved. Furthermore, since the refrigerant passage area of the nozzle part 13a can be enlarged with respect to the case where the liquid phase refrigerant is caused to flow into the nozzle part 13a, the processing of the nozzle part 13a is facilitated. As a result, the manufacturing cost of the ejector 13 can be reduced, and the manufacturing cost of the ejector refrigeration cycle 500 as a whole can be reduced.

  (F) Since the heat dissipation performance of the first radiator 121 and the second radiator 122 can be changed independently during the normal operation mode, for example, the heat dissipation performance of the second radiator 122 and the heat absorption of the suction side evaporator 16 The performance can be easily adapted, and the heat radiation performance of the first and second radiators 121 and 122 and the heat absorption performance of the outflow side evaporator 14 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 13a of the ejector 13 is unnecessarily reduced. You can avoid that. Thereby, the further COP improvement effect can be acquired. The reason is that the amount of recovered energy in the nozzle portion 13a can be increased by unnecessarily reducing the enthalpy of the refrigerant flowing into the nozzle portion 13a.

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

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

  Further, when frost formation occurs in the outflow side evaporator 14 and the suction side evaporator 16, the control device opens the on-off valve 26 so that the high-temperature refrigerant discharged from the first compressor 11 is removed from the suction side evaporator. It is possible to execute a defrosting operation mode in which the defrosting is performed by flowing into the refrigerant 16 and the high-temperature refrigerant discharged from the second compressor 21 is caused to flow into the outflow evaporator 14 to defrost.

  Therefore, it is possible to stably operate the ejector-type refrigeration cycle 500 while avoiding a cycle failure due to frost formation on the outflow side evaporator 14 and the suction side evaporator 16. Furthermore, since the variable throttle mechanism 19 is employed as the pressure reducing means and the throttle opening degree of the variable throttle mechanism 19 is fully closed during the defrosting operation, the refrigerant flowing out of the bypass passage 25 is branched via the variable throttle mechanism 19. It is possible to reliably prevent the flow to the 18 side.

(Thirty-fifth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 53, an example in which the connection mode of the bypass passage 25 is changed with respect to the 34th embodiment will be described.

  Specifically, the bypass passage 25 of the present embodiment is provided between the outlet side of the first radiator 121 and the inlet side of the temperature type expansion valve 17, and between the outlet side of the variable throttle mechanism 19 and the inlet side of the suction side evaporator 16. It is provided to connect between the two. Therefore, the bypass passage 25 constitutes a refrigerant flow path that guides the high-pressure refrigerant in the cycle on the downstream side of the first radiator 121 to the suction-side evaporator 16.

  When the ejector refrigeration cycle 500 of the present embodiment is operated, the normal operation mode operates in the same manner as the Mollier diagram of FIG. 52A of the 34th embodiment. On the other hand, in the defrosting operation mode, the control device stops the first cooling fan 121 a, so the refrigerant discharged from the first compressor 11 does not radiate heat at the first radiator 121. For this reason, it operates similarly to the Mollier diagram of FIG. 52 (b) in the thirty-fourth embodiment also in the defrosting operation mode.

  Therefore, the same effects as those in the 34th embodiment can be obtained in the ejector refrigeration cycle 500 of this embodiment.

(Thirty-sixth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 54, an example in which the connection mode of the bypass passage 25 is changed with respect to the 34th embodiment will be described.

  Specifically, the bypass passage 25 of the present embodiment is provided between the second radiator 122 outlet side and the temperature type expansion valve 17 inlet side, and between the variable throttle mechanism 19 outlet side and the suction side evaporator 16 inlet side. It is provided to connect between the two. Therefore, the bypass passage 25 constitutes a refrigerant flow path that guides the high-pressure refrigerant in the cycle on the downstream side of the second radiator 122 to the suction-side evaporator 16.

  When the ejector-type refrigeration cycle 500 of this embodiment is operated, as in the 35th embodiment, in the normal operation mode, the operation is performed similarly to the Mollier diagram of FIG. 52 (a) of the 34th embodiment, and the defrosting operation is performed. In the mode, the operation is similar to the Mollier diagram of FIG. 52 (b) of the 34th embodiment.

  Therefore, the same effects as those in the 34th embodiment can be obtained in the ejector refrigeration cycle 500 of this embodiment.

(Thirty-seventh embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 55, an example in which the connection mode of the bypass passage 25 is changed with respect to the 34th embodiment will be described. Specifically, the bypass passage 25 of the present embodiment includes a connection pipe 25c that connects the outlet side of the first radiator 121 and the outlet side of the second radiator 122, and the outlet side of the variable throttle mechanism 19 and the suction side evaporator 16. It is provided to connect between the inlet side.

  Further, first and second on-off valves 25d and 25e for opening and closing the connection pipe are provided at both ends of the connection pipe 25c. The first and second opening / closing valves 25d and 25e are electromagnetic valves whose opening / closing operations are controlled by a control signal output from the control device. The control device closes both the first and second on-off valves 25d and 25e during the normal operation mode, and opens both the first and second on-off valves 25d and 25e during the defrosting operation mode.

  Therefore, the bypass passage 25 has a refrigerant flow path that guides the mixed refrigerant of both the high-pressure refrigerant in the cycle on the downstream side of the first radiator 121 and the high-pressure refrigerant in the cycle on the downstream side of the second radiator 122 to the suction-side evaporator 16. It is composed.

  When the ejector-type refrigeration cycle 500 of this embodiment is operated, as in the 35th embodiment, in the normal operation mode, the operation is performed similarly to the Mollier diagram of FIG. 52 (a) of the 34th embodiment, and the defrosting operation is performed. In the mode, the operation is similar to the Mollier diagram of FIG. 52 (b) of the 34th embodiment. Therefore, the same effects as those in the 34th embodiment can be obtained in the ejector refrigeration cycle 500 of this embodiment.

(Thirty-eighth embodiment)
In this embodiment, an example in which a gas-liquid separator 22 is added to the thirty-fourth embodiment will be described as shown in the overall configuration diagram of FIG. The gas-liquid separator 22 is a suction-side gas-liquid separator that separates the gas-liquid refrigerant flowing out from the suction-side evaporator 16 and accumulates excess refrigerant in the cycle.

  When the ejector refrigeration cycle 500 of the present embodiment is operated, it operates similarly to the Mollier diagram of FIG. 52 of the 34th embodiment both in the normal operation mode and in the defrosting operation mode. Therefore, the same effect as in the thirty-fourth embodiment can be obtained.

  Furthermore, even if the liquid refrigerant flows out of the suction side evaporator 16 during the normal operation mode or the high-temperature refrigerant flowing into the suction side evaporator 16 condenses during the defrosting operation mode, the gas-liquid separator Since only the gas-phase refrigerant separated in 22 can be supplied to the second compressor 21, the problem of liquid compression of the second compressor 21 can be avoided.

(Thirty-ninth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 57, an auxiliary bypass passage 25a for guiding the high-pressure refrigerant discharged from the first compression mechanism 11a to the outflow side evaporator 14 is added to the thirty-fourth embodiment. An example will be described.

  More specifically, the auxiliary bypass passage 25a of the present embodiment includes the bypass passage 25 on the downstream side of the on-off valve 26 in the defrosting operation mode, the diffuser portion 13d outlet side and the outlet side evaporator 14 of the ejector 13. It is a refrigerant flow path connecting between the inlet side.

  Further, the auxiliary bypass passage 25a is provided with an auxiliary bypass passage check valve 25b that prohibits the refrigerant flowing out of the diffuser portion 13d of the ejector 13 from flowing toward the bypass passage 25 in the normal operation mode.

  Instead of the auxiliary bypass passage check valve 25b, an auxiliary bypass passage opening / closing valve that opens and closes the auxiliary bypass passage 25a may be employed. In this case, the auxiliary bypass passage opening / closing valve may be closed in the normal operation mode, and the auxiliary bypass passage opening / closing valve may be opened in the defrosting operation mode.

  Therefore, when the ejector refrigeration cycle 500 of the present embodiment is operated, it operates as shown in the Mollier diagram of FIG. 58A in the normal operation mode. The operation in the normal operation mode is the same as the operation in the normal operation mode of the thirty-fourth embodiment (FIG. 52 (a)). 58, the reference numerals indicating the refrigerant state are the same as those in FIG. 52, and only the suffixes are changed.

On the other hand, in the defrosting operation mode, the high-temperature and high-pressure gas-phase refrigerant discharged from the first compressor 11 has the open / close valve 26 opened, so that the bypass passage 25 is similar to the thirty-fourth embodiment. When the gas flows into and passes through the on-off valve 26, it is decompressed and expanded in an isenthalpy manner (k ₅₈ points → l ₅₈ points). The refrigerant flow depressurized by the on-off valve 26 is divided into a refrigerant flow flowing toward the suction-side evaporator 16 and a refrigerant flow flowing toward the auxiliary bypass passage 25a.

The high-temperature and low-pressure gas-phase refrigerant that has flowed out of the on-off valve 26 toward the suction-side evaporator 16 releases heat to the suction-side evaporator 16 (l ₅₈ points → m ₅₈ points). As a result, the suction side evaporator 16 is defrosted. The refrigerant that has dissipated heat in the suction-side evaporator 16 is sucked into the second compressor 21 and compressed (m ₅₈ points → n ₅₈ points).

The refrigerant discharged from the second compressor 21 is depressurized by pressure loss when passing through the refrigerant suction port 13b → mixing part 13c → diffuser part 13d of the ejector (n ₅₇ points → o ₅₇ points). The refrigerant that has flowed out of the diffuser portion 13d merges with the refrigerant that has flowed out of the auxiliary bypass passage 25a and flows into the outflow side evaporator 14 (n ₅₈ points → o ′ ₅₈ points, l ₅₈ points → o ′ ₅₈ points).

Further, the refrigerant that has flowed into the outflow evaporator 14 dissipates the amount of heat to the outflow evaporator 14 (o ′ ₅₈ points → p ₅₈ points). Thereby, the defrosting of the outflow side evaporator 14 is made. The refrigerant having released heat in the discharge side evaporator 14 is compressed again is sucked into the first compressor 11 (p ₅₈ points → k ₅₈ points).

  Since the ejector refrigeration cycle 500 of the present embodiment operates as described above, the same effects as those of the 34th embodiment can be obtained in the normal operation mode. Further, in the defrosting operation mode, not only the same effect as in the thirty-fourth embodiment can be obtained, but also the pressure of the refrigerant flowing into the outflow side evaporator 14 is reduced to protect the outflow side evaporator 14. You can also.

  That is, in this embodiment, the pressure of the refrigerant flowing into the outflow evaporator 14 can be reduced by joining the refrigerant flowing out from the diffuser portion 13d with the refrigerant flowing out from the auxiliary bypass passage 25a.

  Therefore, it is possible to prevent the refrigerant pressure in the outflow side evaporator 14 from exceeding the pressure resistance in the outflow side evaporator 14 and to protect the outflow side evaporator 14. Further, as described above, since the refrigerant pressure in the outflow side evaporator 14 can be reduced, the refrigerant pressure (refrigerant temperature) in the suction side evaporator 16 is increased within the allowable pressure resistance of the suction side evaporator 16. You may let them.

(40th Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 59, an example in which the defrosting operation mode is realized by eliminating the bypass passage 25 and the on-off valve 26 from the thirty-fourth embodiment will be described. When the ejector refrigeration cycle 500 of the present embodiment is operated, it operates as shown in the Mollier diagram of FIG. 60A in the normal operation mode.

  The operation in the normal operation mode is the same as the operation in the normal operation mode of the thirty-fourth embodiment (FIG. 52 (a)). On the other hand, in the defrosting operation mode, the control device operates the first and second electric motors 11b and 21b, the cooling fan 12a, and the blower fan 16a, and further, the throttle opening degree of the variable throttle mechanism 19 is set higher than that in the normal operation mode. increase.

  Thereby, as shown in FIG. 60B, the refrigerant state in the defrosting operation mode changes in the same manner as in the normal operation mode, but the refrigerant evaporation pressure in the suction side evaporator 16 can be defrosted, that is, The refrigerant evaporation temperature can be raised to a temperature higher than 0 ° C.

  Therefore, in the defrosting operation mode of the present embodiment, the refrigerant evaporation temperature in the suction side evaporator 16 can be increased and the suction side evaporator 16 can be defrosted. Furthermore, in the normal operation mode, the same effects as in the normal operation mode of the 34th embodiment can be obtained.

  Furthermore, if an electric expansion valve is employed instead of the temperature expansion valve 17 and the control device increases the throttle opening of the electric expansion valve in the defrosting operation mode, the outflow side evaporator The refrigerant evaporation temperature at 14 can also be increased.

(41st Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 61, the outflow-side evaporator 14 and the blower fan 14a are abolished with respect to the ejector refrigeration cycle 500 of the 34th embodiment, and the internal heat exchanger 30 is replaced. An added example will be described.

  This internal heat exchanger 30 performs heat exchange between the refrigerant flowing out of the second radiator 122 that passes through the high-pressure side refrigerant flow path 30a and the low-pressure side refrigerant of the cycle that passes through the low-pressure side refrigerant flow path 30b. It is. More specifically, the refrigerant that has flowed out of the second radiator 122 in the present embodiment is a refrigerant that circulates in the refrigerant passage from the outlet side of the second radiator 122 to the inlet side of the variable throttle mechanism 19, and is on the low pressure side of the cycle. The refrigerant is a refrigerant sucked into the first compression mechanism 11a.

  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 in the thirty-fourth embodiment.

  Next, the operation of the present embodiment will be described based on the Mollier diagram of FIG. FIG. 62 (a) is a Mollier diagram in the normal operation mode, and FIG. 62 (b) is a Mollier diagram in the defrosting operation mode.

First, the normal operation mode will be described. In the normal operation mode, the refrigerant discharged from the first compressor 11 ( _a62 point in FIG. 62 (a)) is diverted at the branch portion 38 as in the 34th embodiment. And the refrigerant | coolant which flowed out to the 1st radiator 121 side from the branch part 38 is the 1st radiator 121-> temperature type expansion valve 17-> nozzle part 13a of the ejector 13-> diffuser part of the ejector 13 similarly to 34th Embodiment. It flows in the order of 13 (b1 ₆₂ points → c ₆₂ points → d ₆₂ points → e ₆₂ points → f ₆₂ points).

Refrigerant flowing out of the diffuser portion 13d is heated and flows into the low-pressure side refrigerant passage 30b of the internal heat exchanger 30, to increase its enthalpy (f ₆₂ points → g ₆₂ points). Further, the refrigerant flowing out from the low-pressure side refrigerant flow path 30b of the internal heat exchanger 30 is sucked into the first compressor 11 and compressed again (g ₆₂ point → a ₆₂ point).

Meanwhile, the refrigerant flowing from the branch portion 38 to the second radiator 122 is cooled by the second radiator 122 (a ₆₂ point → b2 ₆₂ points), further, the high-pressure side refrigerant flow path 20a of the internal heat exchanger 30 To reduce the enthalpy (b2 ₆₂ points → b2 ′ ₆₂ points).

The refrigerant flowing out from the high-pressure side refrigerant flow path 30a of the internal heat exchanger 30 flows in the order of the variable throttle mechanism 19 → suction side evaporator 16 (b2 ′ ₆₂ points → h ₆₂ points → i), as in the thirty-fourth embodiment. ₆₂ points). Other operations are the same as those in the thirty-fourth embodiment.

Next, the defrosting operation mode will be described. In the defrosting operation mode, the high-temperature and high-pressure gas-phase refrigerant discharged from the first compressor 11 flows into the bypass passage 25 because the on-off valve 26 is open, and the on-off valve 26 is When passing, it expands under reduced pressure in an isenthalpy manner (k ₆₂ points → l ₆₂ points).

  The high-temperature and low-pressure gas-phase refrigerant that has passed through the on-off valve 26 has the throttle opening of the variable throttle mechanism 19 fully closed, so that the high-pressure side refrigerant flow of the internal heat exchanger 30 passes through the variable throttle mechanism 19. It flows into the suction side evaporator 16 without flowing into the path 30a side.

The refrigerant that has flowed into the suction-side evaporator 16 dissipates the amount of heat to the suction-side evaporator 16 (l ₆₂ points → m ₆₂ points). As a result, the suction side evaporator 16 is defrosted. The refrigerant radiated by the suction side evaporator 16 is sucked into the second compressor 21 and compressed (m ₆₂ points → n ₆₂ points).

The refrigerant discharged from the second compressor 21 is depressurized by the pressure loss when passing through the refrigerant suction port 13b → mixing part 13c → diffuser part 13d of the ejector, and the low-pressure side refrigerant flow path 30b of the internal heat exchanger 30. (N ₆₂ points → o ₆₂ points).

Here, in the defrosting operation mode, the on-off valve 26 is opened, and the second cooling fan 122a is stopped. For this reason, the refrigerant that has flowed into the low-pressure side refrigerant flow path 30b of the internal heat exchanger 30 hardly exchanges heat with the refrigerant in the high-pressure side refrigerant flow path 30a. Then, the refrigerant flowing out from the low-pressure side refrigerant flow path 30b is sucked into the first compressor 11 and compressed again (o ₆₂ point → k ₆₂ point).

  Therefore, when the ejector refrigeration cycle 500 of the present embodiment is operated, in the normal operation mode, the cooling action can be exerted by the suction side evaporator 16, and the same effects as (B) to (E) of the 34th embodiment. Can be obtained.

  Furthermore, 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 13a of the ejector 13 is unnecessarily reduced. You can avoid that. Thereby, the further COP improvement effect can be acquired. Further, the enthalpy flowing into the suction-side evaporator 16 can be reduced by the action of the internal heat exchanger 30, and the COP can be further improved.

  Further, when frost formation occurs in the suction side evaporator 16, the control device opens the on-off valve 26 so that the high-temperature refrigerant discharged from the first compressor 11 flows into the suction side evaporator 16 and is removed. A defrosting operation mode for frosting can be executed. Therefore, similarly to the thirty-fourth embodiment, it is possible to avoid the cycle failure due to the frost formation of the suction side evaporator 16, and to stably operate the ejector refrigeration cycle 500.

(Forty-second embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 63, an example in which the connection mode of the bypass passage 25 is changed with respect to the forty-first embodiment will be described.

  Specifically, the bypass passage 25 of the present embodiment is provided between the outlet side of the first radiator 121 and the inlet side of the temperature type expansion valve 17, and between the outlet side of the variable throttle mechanism 19 and the inlet side of the suction side evaporator 16. It is provided to connect between the two. Therefore, the bypass passage 25 constitutes a refrigerant flow path that guides the high-pressure refrigerant in the cycle on the downstream side of the first radiator 121 to the suction-side evaporator 16.

  When the ejector refrigeration cycle 500 of the present embodiment is operated, the normal operation mode operates in the same manner as the Mollier diagram of FIG. 62 (a) of the 41st embodiment. On the other hand, in the defrosting operation mode, the control device stops the first cooling fan 121 a, so the refrigerant discharged from the first compressor 11 does not radiate heat at the first radiator 121. For this reason, also in the defrosting operation mode, it operates similarly to the Mollier diagram of FIG. 62 (b) of the 41st embodiment.

  Therefore, the same effects as those of the forty-first embodiment can be obtained in the ejector refrigeration cycle 500 of the present embodiment.

(43rd embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 64, an example in which the connection mode of the bypass passage 25 is changed with respect to the forty-first embodiment will be described.

  Specifically, the bypass passage 25 of the present embodiment is provided between the second radiator 122 outlet side and the temperature type expansion valve 17 inlet side, and between the variable throttle mechanism 19 outlet side and the suction side evaporator 16 inlet side. It is provided to connect between the two. Therefore, the bypass passage 25 constitutes a refrigerant flow path that guides the high-pressure refrigerant in the cycle on the downstream side of the second radiator 122 to the suction-side evaporator 16.

  When the ejector refrigeration cycle 500 of the present embodiment is operated, as in the 42nd embodiment, in the normal operation mode, it operates in the same manner as the Mollier diagram of FIG. 62 (a) of the 41st embodiment, and the defrosting operation is performed. In the mode, the operation is similar to the Mollier diagram of FIG. 62 (b) of the forty-first embodiment.

  Therefore, the same effects as those of the forty-first embodiment can be obtained in the ejector refrigeration cycle 500 of the present embodiment.

(44th Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 65, an example in which the connection mode of the bypass passage 25 is changed with respect to the forty-first embodiment will be described. Specifically, the bypass passage 25 of the present embodiment includes the connection pipe 25c that connects the outlet side of the first radiator 121 and the outlet side of the second radiator 122, and the variable throttle mechanism 19 as in the thirty-seventh embodiment. It is provided so as to connect between the outlet side and the inlet side of the suction side evaporator 16.

  Further, first and second on-off valves 25d and 25e for opening and closing the connection pipe are provided at both ends of the connection pipe 25c, as in the 37th embodiment. Therefore, the bypass passage 25 has a refrigerant flow path that guides the mixed refrigerant of both the high-pressure refrigerant in the cycle on the downstream side of the first radiator 121 and the high-pressure refrigerant in the cycle on the downstream side of the second radiator 122 to the suction-side evaporator 16. It is composed.

  When the ejector refrigeration cycle 500 of the present embodiment is operated, as in the 42nd embodiment, in the normal operation mode, it operates in the same manner as the Mollier diagram of FIG. 62 (a) of the 41st embodiment, and the defrosting operation is performed. In the mode, the operation is similar to the Mollier diagram of FIG. 62 (b) of the forty-first embodiment.

  Therefore, the same effects as those of the forty-first embodiment can be obtained in the ejector refrigeration cycle 500 of the present embodiment.

(45th embodiment)
In this embodiment, as shown in the overall configuration diagram of FIG. 66, an accumulator 15 similar to the first embodiment and a gas-liquid separator 22 similar to the 38th embodiment are added to the 41st embodiment. Will be explained. Note that the accumulator 15 of this embodiment does not have a liquid-phase refrigerant outlet. Other configurations are the same as those in the forty-first embodiment.

  When the ejector refrigeration cycle 500 of this embodiment is operated, the operation is the same as that of the Mollier diagram of FIG. 62 of the 41st embodiment both in the normal operation mode and in the defrosting operation mode, as in the 42nd embodiment. To do.

  Therefore, the same effects as those of the forty-first embodiment can be obtained in the ejector refrigeration cycle 500 of the present embodiment. Furthermore, since only the gas-phase refrigerant separated by the accumulator 15 can be supplied to the first compressor 11 during the normal operation mode, the problem of liquid compression of the first compressor 11 can be avoided.

  Further, even if the liquid refrigerant flows out of the suction side evaporator 16 or the high temperature refrigerant flowing into the suction side evaporator 16 is condensed in the defrosting operation mode, it is separated by the gas-liquid separator 22. Since only the vapor phase refrigerant can be supplied to the second compressor 21, the problem of liquid compression of the second compressor 21 can be avoided.

(46th Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 67, an example in which the defrosting operation mode is realized by eliminating the bypass passage 25 and the on-off valve 26 with respect to the 41st embodiment will be described. When the ejector refrigeration cycle 500 of the present embodiment is operated, it operates as shown in the Mollier diagram of FIG. 68A in the normal operation mode.

  The operation in the normal operation mode is the same as the operation in the normal operation mode of the 41st embodiment (FIG. 62 (a)). On the other hand, in the defrosting operation mode, the control device operates the first and second electric motors 11b and 21b, the cooling fan 12a, and the blower fan 16a, and further, the throttle opening degree of the variable throttle mechanism 19 is set higher than that in the normal operation mode. increase.

  Thereby, as shown in FIG. 68 (b), although the state of the refrigerant in the defrosting operation mode changes in the same manner as in the normal operation mode, the refrigerant evaporation pressure in the suction side evaporator 16 can be defrosted, that is, The refrigerant evaporation temperature can be raised to a temperature higher than 0 ° C.

  Therefore, in the defrosting operation mode of the present embodiment, the refrigerant evaporation temperature in the suction side evaporator 16 can be increased and the suction side evaporator 16 can be defrosted. Further, in the normal operation mode, the same effect as in the normal operation mode of the forty-first embodiment can be obtained.

(47th embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 69, the outflow-side evaporator 14 and the blower fan 14a are eliminated from the ejector refrigeration cycle 200 of the fifteenth embodiment, and the same as in the twelfth embodiment. An example in which the internal heat exchanger 30 is added will be described.

  More specifically, the refrigerant that has flowed out of the radiator 12 in the present embodiment is a refrigerant that circulates in the refrigerant passage from the auxiliary radiator 12e outlet side to the variable throttle mechanism 19 inlet side, and the low-pressure side refrigerant of the cycle is The refrigerant is sucked into the first compression mechanism 11a. Other configurations are the same as those in the fifteenth embodiment.

  Next, the operation of the present embodiment will be described based on the Mollier diagram of FIG. FIG. 70 (a) is a Mollier diagram in the normal operation mode, and FIG. 70 (b) is a Mollier diagram in the defrosting operation mode.

First, the normal operation mode will be described. In the normal operation mode, the first compressor 11 discharge refrigerant is radiated by the radiator 12 ₍₇₀ points → b ₇₀ points a in FIG. 70 (a)), similarly to the fifteenth embodiment, the shunt at the divergence portion 18 Is done. The high-pressure refrigerant flowing from the branch portion 18 to the nozzle part 13a side, similarly to the fifteenth embodiment, and flows out from the diffuser part 13d ₍₇₀ points b → d ₇₀ points → e ₇₀ points → f ₇₀ points).

Refrigerant flowing out of the diffuser unit 13d, and flows into the low-pressure side refrigerant flow path 30b of the internal heat exchanger 30, to increase its enthalpy ₍₇₀ points f → g ₇₀ points). Further, the refrigerant flows out from the low-pressure side refrigerant flow path 30b of the internal heat exchanger 30 and is sucked into the first compressor 11 and compressed again (g ₇₀ point → a ₇₀ point).

On the other hand, the high-pressure refrigerant that has flowed out from the branch portion 18 to the auxiliary radiator 12e side is further cooled in the auxiliary radiator 12e and the high-pressure side refrigerant flow path 30a of the internal heat exchanger 30, thereby reducing its enthalpy and liquid. It becomes a phase state (b ₇₀ points → b ′ ₇₀ points → b ″ ₇₀ points).

As in the fifteenth embodiment, the refrigerant flowing out from the high-pressure side refrigerant flow path 30a of the internal heat exchanger 30 flows in the order of the variable throttle mechanism 19 → the suction-side evaporator 16 (b ″ ₇₀ points → h ₇₀ points → i ₇₀ points) Other operations are the same as in the fifteenth embodiment.

Next, the defrosting operation mode will be described. In the defrosting operation mode, the high-temperature and high-pressure gas-phase refrigerant discharged from the first compressor 11 flows into the bypass passage 25 because the on-off valve 26 is open, and the on-off valve 26 is When passing through, it expands under reduced pressure in an isenthalpy manner (k ₇₀ points → l ₇₀ points).

  The high-temperature and low-pressure gas-phase refrigerant that has passed through the on-off valve 26 is sucked without flowing into the radiator 12 through the variable throttle mechanism 19 because the throttle opening of the variable throttle mechanism 19 is fully closed. It flows into the side evaporator 16.

The refrigerant that has flowed into the suction-side evaporator 16 dissipates heat to the suction-side evaporator 16 ( ₇₀ points → ₇₀ m points). As a result, the suction side evaporator 16 is defrosted. The refrigerant radiated by the suction side evaporator 16 is sucked into the second compressor 21 and compressed (m ₇₀ points → n ₇₀ points).

The refrigerant discharged from the second compressor 21 is depressurized by the pressure loss when passing through the refrigerant suction port 13b → mixing part 13c → diffuser part 13d of the ejector, and the low-pressure side refrigerant flow path 30b of the internal heat exchanger 30. (N ₇₀ points → o ₇₀ points).

Here, in the defrosting operation mode, the on-off valve 26 is opened, and the cooling fan 12a is stopped. For this reason, the refrigerant that has flowed into the low-pressure side refrigerant flow path 30b of the internal heat exchanger 30 hardly exchanges heat with the refrigerant in the high-pressure side refrigerant flow path 30a. Then, the refrigerant that has flowed out of the low-pressure side refrigerant flow path 30b is sucked into the first compressor 11 and compressed again (o ₇₀ point → k ₇₀ point).

  Therefore, when the ejector refrigeration cycle 200 of the present embodiment is operated, in the normal operation mode, the cooling action can be exerted by the suction side evaporator 16, and the same effects as (B) and (C) of the seventh embodiment are achieved. And the COP improvement effect similar to 15th Embodiment can be acquired. Further, the enthalpy flowing into the suction-side evaporator 16 can be reduced by the action of the internal heat exchanger 30, and the COP can be further improved.

  Further, when frost formation occurs in the suction side evaporator 16, the control device opens the on-off valve 26 so that the high-temperature refrigerant discharged from the first compressor 11 flows into the suction side evaporator 16 and is removed. A defrosting operation mode for frosting can be executed. Therefore, similarly to the fifteenth embodiment, it is possible to avoid the cycle failure due to the frost formation of the suction side evaporator 16, and to stably operate the ejector refrigeration cycle 200.

(Forty-eighth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 71, an example in which the connection mode of the bypass passage 25 is changed with respect to the 47th embodiment will be described.

  Specifically, the bypass passage 25 of the present embodiment is provided between the auxiliary radiator 12e outlet side and the variable throttle mechanism 19 inlet side, and between the variable throttle mechanism 19 outlet side and the suction side evaporator 16 inlet side. Are provided to connect. Therefore, the bypass passage 25 constitutes a refrigerant flow path that guides the high-pressure refrigerant in the cycle downstream of the radiator 12 (specifically, downstream of the auxiliary radiator 12e) to the suction-side evaporator 16.

  When the ejector refrigeration cycle 200 of this embodiment is operated, it operates in the normal operation mode in the same manner as the Mollier diagram of FIG. 70 (a) of the 47th embodiment. On the other hand, in the defrosting operation mode, since the control device stops the cooling fan 12a, the refrigerant discharged from the first compressor 11 does not radiate heat at the radiator 12 and the auxiliary radiator 12e. For this reason, also in the defrosting operation mode, it operates similarly to the Mollier diagram of FIG. 70 (b) of the 47th embodiment.

  Therefore, the same effects as those of the 47th embodiment can be obtained in the ejector refrigeration cycle 200 of this embodiment.

(49th Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 72, an example in which the connection mode of the bypass passage 25 is changed with respect to the 47th embodiment will be described.

  Specifically, the bypass passage 25 of the present embodiment is between the radiator 12 outlet side and the auxiliary radiator 12e inlet side, and between the variable throttle mechanism 19 outlet side and the suction side evaporator 16 inlet side. It is provided to connect. Therefore, the bypass passage 25 constitutes a refrigerant flow path that guides the high-pressure refrigerant of the cycle downstream of the radiator 12 to the suction-side evaporator 16.

  When the ejector refrigeration cycle 200 of this embodiment is operated, as in the 48th embodiment, in the normal operation mode, the operation is performed similarly to the Mollier diagram of FIG. 70 (a) of the 47th embodiment, and the defrosting operation is performed. In the mode, the operation is the same as the Mollier diagram of FIG. 70 (b) of the 47th embodiment.

  Therefore, the same effects as those of the 47th embodiment can be obtained in the ejector refrigeration cycle 200 of this embodiment.

(50th Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 73, an example in which an accumulator 15 similar to the first embodiment and a gas-liquid separator 22 similar to the eighteenth embodiment are added to the 47th embodiment. Will be explained. Note that the accumulator 15 of this embodiment does not have a liquid-phase refrigerant outlet. Other configurations are the same as those in the 47th embodiment.

  When the ejector refrigeration cycle 200 of this embodiment is operated, it operates similarly to the Mollier diagram of FIG. 70 of the 47th embodiment both in the normal operation mode and in the defrosting operation mode. Therefore, the same effect as that of the 47th embodiment can be obtained.

  Furthermore, since only the gas-phase refrigerant separated by the accumulator 15 can be supplied to the first compressor 11 during the normal operation mode, the problem of liquid compression of the first compressor 11 can be avoided. Further, even if the liquid refrigerant flows out of the suction side evaporator 16 or the high temperature refrigerant flowing into the suction side evaporator 16 is condensed in the defrosting operation mode, it is separated by the gas-liquid separator 22. Since only the vapor phase refrigerant can be supplied to the second compressor 21, the problem of liquid compression of the second compressor 21 can be avoided.

(51st Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 74, an example in which the defrosting operation mode is realized by eliminating the bypass passage 25 and the on-off valve 26 from the 47th embodiment will be described. When the ejector refrigeration cycle 200 of the present embodiment is operated, it operates as shown in the Mollier diagram of FIG. 75A in the normal operation mode.

  The operation in the normal operation mode is the same as the operation in the normal operation mode of the 47th embodiment (FIG. 70 (a)). On the other hand, in the defrosting operation mode, the control device operates the first and second electric motors 11b and 21b, the cooling fan 12a, and the blower fan 16a, and further, the throttle opening degree of the variable throttle mechanism 19 is set higher than that in the normal operation mode. increase.

  Thereby, as shown in FIG. 75 (b), the refrigerant state in the defrosting operation mode changes in the same manner as in the normal operation mode, but the refrigerant evaporation pressure in the suction side evaporator 16 can be defrosted, that is, The refrigerant evaporation temperature can be raised to a temperature higher than 0 ° C.

  Therefore, in the defrosting operation mode of the present embodiment, the refrigerant evaporation temperature in the suction side evaporator 16 can be increased and the suction side evaporator 16 can be defrosted. Further, in the normal operation mode, the same effect as in the normal operation mode of the 47th embodiment can be obtained.

(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, switching between the normal operation mode and the defrosting operation mode is performed based on the operation signal of the changeover switch of the operation panel, but switching between the normal operation mode and the defrosting operation mode is performed. 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.

  (2) In each of the above-described embodiments, examples in which separate compressors are employed as the first and second compressors 11 and 21 have been described. However, the first and second compression mechanisms 11a and 21a are described. The first and second electric motors 11b and 21b may be integrally configured.

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

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

  (3) In each of the above-described embodiments, an example in which an electric compressor is employed as the first and second compressors 11 and 21 has been described. However, the types of the first and second compressors 11 and 21 are limited to this. Not.

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

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

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

  Further, in the above-described embodiment, as the high pressure side pressure reducing means, the temperature type expansion valve 17 that adjusts the superheat degree of the outlet side evaporator 14 outlet side refrigerant to be a predetermined value set in advance is adopted. You may employ | adopt the temperature type expansion valve adjusted so that the superheat degree of the suction side evaporator 16 outlet side refrigerant | coolant may become the predetermined value set beforehand.

  Further, as the high pressure side pressure reducing means, an electric expansion valve whose throttle opening (valve opening) can be adjusted by an external electric control signal may be adopted, or a fixed throttle without adopting a variable throttle mechanism. A mechanism may be employed. Furthermore, in the above-described first to sixth and fifteenth to twentieth embodiments, a high-pressure side decompression unit may be provided.

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

  For example, if the ejector-type refrigeration cycle 100, 200 not provided with the high-pressure side pressure reducing means as in the first to sixth and fifteenth to twentieth embodiments is configured as a supercritical refrigeration cycle, the high-pressure side refrigerant pressure increases. The pressure difference between the nozzle part 13a inlet side pressure and the nozzle part 13a outlet side pressure of the ejector 13 becomes large.

  Thereby, the difference of the enthalpy of the nozzle part 13a inlet side refrigerant | coolant and the enthalpy of the nozzle part 13a outlet side refrigerant | coolant increases, and it can increase recovery amount of energy. Of course, the other ejector refrigeration cycles 200 to 500 can be configured as a supercritical refrigeration cycle, and the same effect can be obtained by eliminating the high-pressure side decompression means.

  Further, when the ejector-type refrigeration cycle 100 to 500 is a supercritical refrigeration cycle, the high-pressure side refrigerant pressure is set as the high-pressure side decompression means, and the COP is substantially maximum 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.

  As such a pressure control valve, specifically, there is a temperature sensing portion provided on the outlet side of the radiator 12 (first radiator 121), and the high pressure on the outlet side of the radiator 12 is inside the temperature sensing portion. It is possible to employ a configuration in which a pressure corresponding to the temperature of the refrigerant is generated and the valve opening is adjusted by a mechanical mechanism in accordance with the balance between the internal pressure of the temperature sensing portion and the refrigerant pressure on the outlet side of the radiator 12.

  (6) In the above-described embodiment, the throttle mechanism is adopted as the high pressure side pressure reducing means and the low pressure side pressure reducing means. However, the refrigerant is used as the high pressure side pressure reducing means and the low pressure side pressure reducing means (variable throttle mechanisms 19, 29). You may employ | adopt the expander which converts the pressure energy of a refrigerant | coolant into mechanical energy, and outputs it while decompressing by volume expansion.

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

  For example, if a rotary positive displacement compression mechanism is employed as an expander, rotational energy can be output as mechanical energy. Furthermore, if the mechanical energy output from the expander is used as an auxiliary power source for the first and second compression mechanisms, for example, the energy efficiency of the ejector refrigeration cycle 100 to 500 as a whole can be improved.

  The mechanical energy output from the expander may be used as a power source for external equipment. For example, if a generator is adopted as an external device, electric energy can be obtained. Moreover, if a flywheel is employ | adopted as an external apparatus, the mechanical energy output from the expander can be stored as a kinetic energy. Moreover, if a stroking device (spring spring) is employed as an external device, the mechanical energy output from the expander 20 can be stored as elastic energy.

  (7) In the above-described embodiment, as the radiator 12 (the first and second radiators 121 and 122), the condensing heat exchange unit that condenses the refrigerant, and the gas-liquid refrigerant condensed in the condensing heat exchange unit are used. You may employ | adopt what is called a subcool type | mold condenser which comprised integrally the gas-liquid separation part to isolate | separate and the supercooling heat exchange part which supercools the liquid phase refrigerant | coolant isolate | separated in the gas-liquid separation part.

  For example, as the radiator 12 of the fifteenth to twentieth embodiments, a subcool condenser is adopted, the heat exchanger for condensation is used as the radiator 12, and the branch portion 18 is configured in the gas-liquid separator, The subcooling heat exchange section may be used as the auxiliary radiator 12e.

  (8) The means described in the above embodiments can be applied to other embodiments. For example, in the first to sixth, twelfth to fourteenth and forty-first to forty-first embodiments, the outflow side evaporator 14 is not provided, but in these embodiments, the outflow side evaporator 14 may be provided. . In this case, the outflow side evaporator 14 can be used for cooling in the refrigerator.

  For example, in the seventh to 51st embodiments, as in the second embodiment, the fixed throttle 19a and the check valve 19b may be employed as the suction side pressure reducing means, or a pressure reducing mechanism integrated check valve may be used. It may be adopted.

  Furthermore, you may add an outflow side gas-liquid separator and a suction side gas-liquid separator with respect to each embodiment which does not provide the outflow-side gas-liquid separator and the suction-side gas-liquid separator. Furthermore, the heating means (electric heater 16b) described in the sixth embodiment may be applied to other embodiments. Furthermore, in the seventh to 25th embodiments, the high pressure side pressure reducing means may be arranged in the refrigerant passage from the outlet of the branching portion 18 to the inlet of the nozzle portion 13a of the ejector 13.

  (9) In the above seventh to eleventh and fifteenth to fortieth embodiments, the cooling target spaces (refrigerant space, freezer space) that are different in the outflow side evaporator 14 and the suction side evaporator 16 are cooled. However, the same cooling target space may be cooled. In this case, it is desirable that the outflow side evaporator 14 and the suction side evaporator 16 are assembled in an integrated structure, and the air blown from the blower fan is passed in the order of the outflow side evaporator 14 → the suction side evaporator 16.

  This is because the refrigerant evaporation pressure (refrigerant evaporation temperature) of the suction side evaporator 16 is lower than the refrigerant evaporation pressure (refrigerant evaporation temperature) of the outflow side evaporator 14. That is, by passing the blown air from the blower fan as described above, a temperature difference between the refrigerant evaporation temperature of the outflow side evaporator 14 and the suction side evaporator 16 and the blown air is secured, and the blown air is efficiently flowed. Can be cooled.

  Further, as a specific means for assembling the outflow side evaporator 14 and the suction side evaporator 16 into an integral structure, for example, the constituent parts of both the evaporators 14 and 16 are made of aluminum and integrated with a joining means such as brazing. You may join to. Furthermore, the structure couple | bonded integrally by mechanical engagement means, such as bolting, may be sufficient.

  Further, as the outflow side evaporator 14 and the suction side evaporator 16, a fin-and-tube type heat exchanger is adopted, and the fins of the outflow side evaporator 14 and the suction side evaporator 16 are made common so that the refrigerant can pass therethrough. It is good also as a structure which divides | segments into two evaporators by a path | pass structure (flow path structure).

  Further, when the outflow side evaporator 14 and the suction side evaporator 16 are configured to cool the same freezer, the refrigerant evaporation temperature of the suction side evaporator 16 arranged downstream of the blown air flow becomes frosted. The resulting temperature (below 0 ° C.) is reached. On the other hand, the absolute humidity of the blown air flowing into the suction side evaporator 16 can be reduced in advance by adjusting the refrigerant evaporation temperature in the outflow side evaporator 14.

  Thereby, generation | occurrence | production of the frost in the suction side evaporator 16 can be suppressed. Furthermore, since the flow of the blast air due to frost formation can be prevented, the fin pitch and the like of the suction side evaporator 16 can be reduced to reduce the size of the suction side evaporator 16.

  (10) In the above-described twelfth to fourteenth, twenty-first to twenty-fifth and forty-first to forty-first embodiments, the example in which the internal heat exchangers 30 and 31 are employed has been described. 31 may employ a counter-flow 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, or the refrigerant in the high-pressure side refrigerant flow path. You may employ | adopt the parallel flow type heat exchanger from which the flow direction and the refrigerant | coolant flow direction in a low voltage | pressure side refrigerant flow path become the same direction.

  Further, in the first to eleventh, fifteenth to twentieth and twenty-sixth to forty embodiments described above, the high-pressure side refrigerant of the cycle that has flowed out of the radiator 12 (the first radiator 121 and the second radiator 122) An internal heat exchanger that exchanges heat with the low-pressure side refrigerant of the cycle may be employed. In this case, as the high-pressure side refrigerant of the cycle, the refrigerant in the refrigerant passage from the radiator 12 to the high-pressure side decompression means, the refrigerant from the radiator 12 to the suction-side decompression means, the inlet side of the nozzle portion 13a of the ejector 13 from the radiator 12 Refrigerant leading to can be adopted.

  Furthermore, as the low-pressure side refrigerant in the cycle flowing through the internal heat exchangers 30 and 31, either the refrigerant sucked into the first compressor 11 or the refrigerant sucked into the second compressor 21 may be adopted.

  (11) In the thirty-third to thirty-third embodiments described above, 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 18 and 28 may be configured by three-way valves to switch the refrigerant flow path.

  Further, as the first and second suction side pressure reducing means, a fixed throttle mechanism is adopted, and the first and second suction side pressure reducing means or between the first and second suction side pressure reducing means or the first and second pressure reducing means. An electromagnetic valve (open / close valve) for opening and closing the flow path may be provided on the downstream side of the suction side pressure reducing means.

  (12) In the above-described embodiment, the ejector refrigeration cycles 100 to 500 including only the first and second compression mechanisms 11a and 21a have been described. However, an additional compression mechanism may be provided. For example, an additional evaporator may be provided in parallel with the suction-side evaporator 16 so that only the refrigerant flowing out of the evaporator is sucked and compressed.

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

  (14) In each of the above-described embodiments, the outflow side evaporator 14 and the suction side evaporator 16 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. In addition, the outflow side evaporator 14 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 heats the heated refrigerant such as air or water. It is good also as a heat pump cycle comprised as a vessel.

It is a whole block diagram of the ejector-type refrigerating cycle of 1st Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the ejector refrigeration cycle of the first embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode. . It is a whole block diagram of the ejector type refrigerating cycle of 2nd Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 3rd Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 4th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 5th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the fifth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the fifth embodiment. . It is a whole block diagram of the ejector-type refrigerating cycle of 6th Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 7th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the seventh embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the seventh embodiment. . It is a whole block diagram 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 whole block diagram of the ejector-type refrigerating cycle of 10th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the tenth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the tenth embodiment. . It is a whole block diagram of the ejector type refrigerating cycle of 11th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the eleventh embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the eleventh embodiment. . It is a whole block diagram of the ejector type refrigerating cycle of 12th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the twelfth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the twelfth embodiment. . It is a whole block diagram of the ejector-type refrigerating cycle of 13th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 14th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the fourteenth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the fourteenth embodiment. . It is a whole block diagram of the ejector type refrigerating cycle of 15th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the fifteenth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the fifteenth embodiment. . It is a whole block diagram of the ejector-type refrigerating cycle of 16th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 17th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 18th Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 19th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the nineteenth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the nineteenth embodiment. . It is a whole block diagram of the ejector-type refrigerating cycle of 20th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the twentieth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the twentieth embodiment. . It is a whole block diagram of the ejector-type refrigerating cycle of 21st Embodiment. (A) is a Mollier diagram which shows the state of the refrigerant | coolant in the normal operation mode of 21st Embodiment, (b) is the Mollier diagram which shows the state of the refrigerant | coolant in the defrost operation mode of 21st Embodiment. . It is a whole block diagram of the ejector type refrigerating cycle of 22nd Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 23rd Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 24th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the twenty-fourth embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the twenty-fourth embodiment. . It is a whole block diagram of the ejector-type refrigerating cycle of 25th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the 25th embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the 25th embodiment. . It is a whole block diagram of the ejector type refrigerating cycle of 26th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the 26th embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the 26th embodiment. (C) is a Mollier diagram which shows the state of the refrigerant | coolant in 2nd defrost operation mode. It is a whole block diagram of the ejector type refrigerating cycle of 27th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 28th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 29th Embodiment. (A) is a Mollier diagram which shows the state of the refrigerant | coolant in the normal operation mode of 29th Embodiment, (b) is the Mollier diagram which shows the state of the refrigerant | coolant in the defrost operation mode of 29th Embodiment. . It is a whole block diagram of the ejector type refrigerating cycle of 30th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the 30th embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the 30th embodiment. (C) is a Mollier diagram which shows the state of the refrigerant | coolant in 2nd defrost operation mode. It is a whole block diagram of the ejector-type refrigerating cycle of 31st Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 32nd Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 33rd Embodiment. (A) is a Mollier diagram which shows the state of the refrigerant | coolant in the normal operation mode of 33rd Embodiment, (b) is the Mollier diagram which shows the state of the refrigerant | coolant in the defrost operation mode of 33rd Embodiment. . It is a whole block diagram of the ejector type refrigerating cycle of 34th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the 34th embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the 34th embodiment. . It is a whole block diagram of the ejector type refrigerating cycle of 35th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 36th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 37th Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 38th Embodiment. It is a whole block diagram of the ejector-type refrigeration cycle of the 39th embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the 39th embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the 39th embodiment. . It is a whole block diagram of the ejector type refrigerating cycle of 40th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the 40th embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the 40th embodiment. . It is a whole block diagram of the ejector-type refrigerating cycle of 41st Embodiment. (A) is a Mollier diagram which shows the state of the refrigerant | coolant in the normal operation mode of 41st Embodiment, (b) is the Mollier diagram which shows the state of the refrigerant | coolant in the defrost operation mode of 41st Embodiment. . It is a whole block diagram of the ejector type | mold refrigerating cycle of 42nd Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 43rd Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 44th Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 45th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 46th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the 46th embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the 46th embodiment. . It is a whole block diagram of the ejector type refrigerating cycle of 47th Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the 47th embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the 47th embodiment. . It is a whole block diagram of the ejector type refrigerating cycle of 48th Embodiment. It is a whole block diagram of the ejector type | mold refrigerating cycle of 49th Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 50th Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 51st Embodiment. (A) is a Mollier diagram showing the state of the refrigerant in the normal operation mode of the 51st embodiment, and (b) is a Mollier diagram showing the state of the refrigerant in the defrosting operation mode of the 51st embodiment. . It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of a prior art.

Explanation of symbols

11, 12 1st, 2nd compressor 11a, 21a 1st, 2nd compression mechanism 11b, 21b 1st, 2nd electric motor 12, 121, 122 Radiator, 1st, 2nd radiator 12a, 121a, 122a Cooling fan, first and second cooling fans 12e Auxiliary radiator 13 Ejector 13a Nozzle part 13b Refrigerant suction port 13d Diffuser part 14 Outflow side evaporator 15 Accumulator 16 Suction side evaporator 17 Thermal expansion valve 18, 28, 38 First , 2nd branch part, branch part 19, 29 1st, 2nd variable throttle mechanism 22 Gas-liquid separator 25, 25a Bypass passage, auxiliary bypass passage 26 On-off valve 30, 31 Internal heat exchanger

Claims (43)

  A first compression mechanism (11a) that compresses and discharges the refrigerant, a radiator (12) that radiates high-pressure refrigerant discharged from the first compression mechanism (11a), and a refrigerant that flows out of the radiator (12) The refrigerant is sucked by the flow of the high-speed injection refrigerant that is injected from the branch portion (18) that branches the flow of the refrigerant and the nozzle portion (13a) that decompresses and expands one of the refrigerant branched at the branch portion (18). An ejector (13) that sucks through the port (13b) and pressurizes the mixed refrigerant of the jetted refrigerant and the suctioned refrigerant sucked from the refrigerant suction port (13b) at a diffuser unit (13d); 18) The suction side decompression means (19) for decompressing and expanding the other refrigerant branched in 18), the refrigerant decompressed and expanded by the suction side decompression means (19) is evaporated, and the refrigerant suction port (13b) Spill to the side A suction side evaporator (16), a second compression mechanism (21a) for sucking and compressing the suction side evaporator (16) outlet side refrigerant and discharging it to the refrigerant suction port (13b) side, and a high pressure of the cycle An ejector refrigeration cycle, comprising: a bypass passage (25) for guiding the side refrigerant to the suction side evaporator (16); and an opening / closing means (26) for opening and closing the bypass passage (25).   The ejector refrigeration cycle according to claim 1, further comprising an outflow side evaporator (14) for evaporating the refrigerant flowing out of the diffuser section (13d).   The ejector refrigeration cycle according to claim 2, further comprising an auxiliary bypass passage (25a) for guiding the high-pressure side refrigerant of the cycle to the outflow side evaporator (14).   The high-pressure side refrigerant in the cycle is a refrigerant on the upstream side of the radiator (12), and the bypass passage (25) bypasses the radiator (12) to be upstream of the radiator (12). The ejector refrigeration cycle according to any one of claims 1 to 3, wherein the refrigerant is guided to the suction side evaporator (16).   A heat radiation capacity adjusting means (12a) for adjusting the heat radiation capacity of the heat radiator (12) is provided, wherein the high-pressure side refrigerant of the cycle is a refrigerant on the downstream side of the heat radiator (12), and the heat radiation capacity adjusting means ( 12a), when the opening / closing means (26) opens the bypass passage (25), the heat dissipation capability of the radiator (12) is reduced. The ejector-type refrigeration cycle described in 1.   A high pressure side pressure reducing means (17) is provided in a refrigerant passage extending from the radiator (12) outlet side to the nozzle part (13a) inlet side, and decompresses and expands the refrigerant flowing out of the radiator (12). The ejector refrigeration cycle according to any one of claims 1 to 5, wherein   The ejector-type refrigeration according to claim 6, wherein the high-pressure side pressure reducing means (17) is disposed in a refrigerant passage extending from the radiator (12) outlet side to the branch portion (18) inlet side. cycle.   An internal heat exchanger (30) for exchanging heat between the refrigerant flowing out of the radiator (12) and the low-pressure side refrigerant of the cycle when the opening / closing means (26) closes the bypass passage (25); The ejector refrigeration cycle according to any one of claims 1 to 7, wherein   The refrigerant that has flowed out of the radiator (12) is a refrigerant that flows in a refrigerant passage extending from the outlet side of the branch part (18) to the inlet side of the suction side pressure reducing means (19). The ejector refrigeration cycle described.   When the opening / closing means (26) closes the bypass passage (25), the internal heat exchanger (31) exchanges heat between the refrigerant in the decompression and expansion process in the suction side decompression means (19) and the low-pressure side refrigerant in the cycle. The ejector-type refrigeration cycle according to claim 1, further comprising:   The ejector refrigeration cycle according to any one of claims 8 to 10, wherein the low-pressure side refrigerant of the cycle is a refrigerant sucked into the first compression mechanism (11a).   The ejector refrigeration cycle according to any one of claims 8 to 10, wherein the low-pressure side refrigerant of the cycle is a refrigerant sucked into the second compression mechanism (21a).   Arranged on the downstream side of the refrigerant flow of the branch portion (18), when the opening / closing means (26) closes the bypass passage (25), the refrigerant flowing into the suction side pressure reducing means (19) is radiated. The ejector refrigeration cycle according to any one of claims 1 to 12, further comprising an auxiliary radiator (12e).   A suction-side gas-liquid separator (22) disposed between the suction-side evaporator (16) and the second compression mechanism (21a) for separating the gas-liquid refrigerant; The ejector refrigeration cycle according to any one of claims 1 to 13, wherein a gas-phase refrigerant outlet of the vessel (22) is connected to the suction port side of the second compression mechanism (21a).   A first compression mechanism (11a) that compresses and discharges the refrigerant, a radiator (12) that radiates high-pressure refrigerant discharged from the first compression mechanism (11a), and a refrigerant that flows out of the radiator (12) Refrigerant sucked from the refrigerant suction port (13b) by the flow of the high-speed jet refrigerant jetted from the nozzle portion (13a) that decompresses and expands the suction refrigerant and the suction refrigerant sucked from the refrigerant suction port (13b) An ejector (13) for increasing the pressure of the mixed refrigerant at the diffuser section (13d), a branch section (18) for branching the flow of the refrigerant flowing out from the diffuser section (13d), and the branch section (18) One of the branched refrigerants is evaporated and the first compression mechanism (11a) is discharged to the suction side. The outflow side evaporator (14) and the other refrigerant branched at the branching part (18) are decompressed and expanded. Let A suction-side decompression means (19), a suction-side evaporator (16) for evaporating the refrigerant decompressed and expanded by the suction-side decompression means (19) and flowing it out to the refrigerant suction port (13b) side; The suction side evaporator (16) sucks and compresses the outlet side refrigerant and discharges it to the refrigerant suction port (13b) side, and the high pressure side refrigerant of the cycle is sent to the suction side evaporator ( 16) An ejector-type refrigeration cycle comprising a bypass passage (25) leading to 16) and an opening / closing means (26) for opening and closing the bypass passage (25).   The suction side pressure reducing means (19) is constituted by a variable throttle mechanism that reduces the throttle opening when the opening / closing means (26) closes the bypass passage (25). 15. The ejector type refrigeration cycle according to 15.   The suction side pressure reducing means (19) comprises a variable throttle mechanism that increases a throttle opening when the opening / closing means (26) closes the bypass passage (25). 15. The ejector type refrigeration cycle according to 15.   The high-pressure side refrigerant in the cycle is a refrigerant on the upstream side of the radiator (12), and the bypass passage (25) bypasses the radiator (12) to be upstream of the radiator (12). The ejector refrigeration cycle according to any one of claims 15 to 17, wherein the refrigerant is guided to the suction side evaporator (16).   A heat radiation capacity adjusting means (12a) for adjusting the heat radiation capacity of the radiator (12) is provided, and the high-pressure side refrigerant of the cycle is a refrigerant on the downstream side of the heat radiator (12), and the heat radiation capacity adjusting means ( 12a), wherein when the opening and closing means (26) opens the bypass passage (25), the heat dissipation capability of the radiator (12) is reduced. The ejector-type refrigeration cycle described in 1.   A high pressure side pressure reducing means (17) is provided in a refrigerant passage extending from the radiator (12) outlet side to the nozzle part (13a) inlet side, and decompresses and expands the refrigerant flowing out of the radiator (12). The ejector type refrigeration cycle according to any one of claims 15 to 19, wherein   A suction-side gas-liquid separator (22) disposed between the suction-side evaporator (16) and the second compression mechanism (21a) for separating the gas-liquid refrigerant; The ejector refrigeration cycle according to any one of claims 15 to 20, wherein a gas phase refrigerant outlet of the vessel (22) is connected to the suction port side of the second compression mechanism (21a).   A first compression mechanism (11a) that compresses and discharges the refrigerant, a radiator (12) that radiates high-pressure refrigerant discharged from the first compression mechanism (11a), and a refrigerant that flows out of the radiator (12) Refrigerant sucked from the refrigerant suction port (13b) by the flow of the high-speed jet refrigerant jetted from the nozzle portion (13a) that decompresses and expands the suction refrigerant and the suction refrigerant sucked from the refrigerant suction port (13b) And an ejector (13) for increasing the pressure of the mixed refrigerant at the diffuser section (13d), and an outflow side for evaporating the refrigerant flowing out from the diffuser section (13) and flowing out to the suction side of the first compression mechanism (11a) An evaporator (14), a first branch part (18) configured to be able to branch the flow of the refrigerant flowing out of the radiator (12), and the refrigerant branched by the first branch part (18) Decompression expansion The first suction-side pressure reducing means (19), the second branch portion (28) configured to be able to branch the flow of the refrigerant flowing out from the diffuser portion (13), and the second branch portion (28) Second suction side pressure reducing means (29) for decompressing and expanding the branched refrigerant, refrigerant flowing out from the first suction side pressure reducing means (19), and refrigerant flowing out from the second suction side pressure reducing means (29) A suction side evaporator (16) that evaporates at least one of the refrigerants and flows out to the refrigerant suction port (13b) side, and sucks and compresses the suction side evaporator (16) outlet side refrigerant, A second compression mechanism (21a) that discharges toward the refrigerant suction port (13b), a bypass passage (25) that guides the high-pressure side refrigerant of the cycle to the suction-side evaporator (16), and the bypass passage (25) Opening and closing means (26) for opening and closing Ejector refrigeration cycle, characterized in that to obtain.   The second suction side pressure reducing means (29) is constituted by a variable throttle mechanism that reduces the throttle opening when the opening / closing means (26) closes the bypass passage (25). The ejector-type refrigeration cycle according to claim 22.   The second suction side pressure reducing means (29) is constituted by a variable throttle mechanism that increases the throttle opening when the opening / closing means (26) closes the bypass passage (25). The ejector-type refrigeration cycle according to claim 22.   The high-pressure side refrigerant in the cycle is a refrigerant on the upstream side of the radiator (12), and the bypass passage (25) bypasses the radiator (12) to be upstream of the radiator (12). The ejector refrigeration cycle according to any one of claims 22 to 24, wherein the refrigerant is guided to the suction side evaporator (16).   A heat radiation capacity adjusting means (12a) for adjusting the heat radiation capacity of the radiator (12) is provided, and the high-pressure side refrigerant of the cycle is a refrigerant on the downstream side of the heat radiator (12), and the heat radiation capacity adjusting means ( 25a) 12a), wherein when the opening and closing means (26) opens the bypass passage (25), the heat dissipation capability of the radiator (12) is reduced. The ejector-type refrigeration cycle described in 1.   A high pressure side pressure reducing means (17) disposed in a refrigerant passage extending from the outlet side of the first branch part (18) to the inlet side of the nozzle part (13a) and decompressing and expanding the refrigerant flowing out of the radiator (12). The ejector refrigeration cycle according to any one of claims 22 to 26, further comprising:   A suction-side gas-liquid separator (22) disposed between the suction-side evaporator (16) and the second compression mechanism (21a) for separating the gas-liquid refrigerant; The ejector refrigeration cycle according to any one of claims 22 to 27, wherein a gas-phase refrigerant outlet of the container (22) is connected to the suction port side of the second compression mechanism (21a).   The first compression mechanism (11a) that compresses and discharges the refrigerant, the branch portion (38) that branches the flow of the high-pressure refrigerant discharged from the first compression mechanism (11a), and the branch portion (38) The first radiator (121) that radiates one of the branched refrigerants and the flow of the high-speed injected refrigerant that is injected from the nozzle portion (13a) that decompresses and expands the refrigerant that has flowed out of the first radiator (121). An ejector (13) for sucking the refrigerant from the refrigerant suction port (13b) and increasing the pressure of the mixed refrigerant of the jetted refrigerant and the suction refrigerant sucked from the refrigerant suction port (13b) at the diffuser portion (13d); A second radiator (122) that radiates the other refrigerant branched by the branch portion (38), and a suction-side decompression means (19) that decompresses and expands the refrigerant flowing out of the second radiator (122). The suction side The suction side evaporator (16) that evaporates the refrigerant flowing out from the pressure means (19) and flows out to the refrigerant suction port (13b) side, and the suction side evaporator (16) outlet side refrigerant are sucked and compressed. A second compression mechanism (21a) that discharges to the refrigerant suction port (13b) side, a bypass passage (25) that guides the high-pressure side refrigerant of the cycle to the suction-side evaporator (16), and the bypass passage ( And an opening / closing means (26) for opening and closing 25).   30. The ejector-type refrigeration cycle according to claim 29, further comprising an outflow side evaporator (14) for evaporating the refrigerant flowing out of the diffuser section (13d).   The ejector refrigeration cycle according to claim 30, further comprising an auxiliary bypass passage (25a) for guiding the high-pressure side refrigerant of the cycle to the outflow evaporator (14).   The high-pressure side refrigerant of the cycle is a refrigerant on the upstream side of the first radiator (121) and the second radiator (122), and the bypass passage (25) includes the first radiator (121) and 32. The method according to any one of claims 29 to 31, wherein the second radiator (122) is bypassed and the refrigerant on the upstream side of the radiator (12) is guided to the suction side evaporator (16). The ejector refrigeration cycle described.   The first heat radiator (121) includes a first heat radiation capacity adjusting means (121a) for adjusting a heat radiation capacity, and the high-pressure side refrigerant of the cycle is a refrigerant on the downstream side of the first heat radiator (121), The first heat dissipating capacity adjusting means (121a) is configured such that when the bypass passage (25) guides the refrigerant on the downstream side of the first heat radiator (121) to the suction side evaporator (16), the first heat radiator The ejector-type refrigeration cycle according to any one of claims 29 to 31, wherein the heat dissipation capability of (121) is reduced.   A second heat dissipating capacity adjusting means (122a) for adjusting a heat dissipating capacity of the second heat dissipator (122); and the high pressure side refrigerant of the cycle is a refrigerant downstream of the second heat dissipator (122), The second heat dissipating capacity adjusting means (122a) is configured such that when the bypass passage (25) guides the refrigerant on the downstream side of the first heat radiator (122) to the suction side evaporator (16), the first heat radiator The ejector refrigeration cycle according to any one of claims 29 to 31, wherein the heat dissipation capability of (122) is reduced.   The first and second heat radiators (121, 122) are provided with first and second heat radiation capacity adjusting means (121a, 122a) for adjusting the heat radiation capacity of the first and second heat radiators (121, 122). It is a refrigerant | coolant of the at least one downstream among heat radiators (122), Comprising: As for the said 1st, 2nd heat radiation capability adjustment means (121a, 122a), the said bypass channel (25) is said 1st heat radiator (122). 32. Any one of claims 29 to 31, wherein when the downstream refrigerant is led to the suction side evaporator (16), the heat radiation capacity of the first and second heat radiators (121, 122) is reduced. The ejector type refrigeration cycle according to claim 1.   An internal heat exchanger (30) for exchanging heat between the refrigerant flowing out of the second radiator (122) and the low-pressure side refrigerant of the cycle when the opening / closing means (26) closes the bypass passage (25). 36. The ejector refrigeration cycle according to any one of claims 29 to 35, further comprising:   The ejector-type refrigeration cycle according to claim 36, wherein the low-pressure side refrigerant of the cycle is a refrigerant sucked into the first compression mechanism (11a).   38. The ejector refrigeration cycle according to claim 37, wherein the low-pressure side refrigerant of the cycle is a refrigerant sucked into the second compression mechanism (21a).   A high-pressure side pressure reducing means (17) disposed in a refrigerant passage from the outlet side of the first radiator (121) to the inlet side of the nozzle part (13a) and decompressing and expanding the refrigerant flowing out of the first radiator (121). The ejector refrigeration cycle according to any one of claims 29 to 38, further comprising:   A suction-side gas-liquid separator (22) disposed between the suction-side evaporator (16) and the second compression mechanism (21a) for separating the gas-liquid refrigerant; The ejector refrigeration cycle according to any one of claims 29 to 38, wherein a gas-phase refrigerant outlet of the container (22) is connected to the suction port side of the second compression mechanism (21a).   First discharge capacity changing means (11b) for changing the refrigerant discharge capacity of the first compression mechanism (11a), and second discharge capacity changing means (21b) for changing the refrigerant discharge capacity of the second compression mechanism (21a). The first discharge capacity changing means (11b) and the second discharge capacity changing means (21b) are each independently a refrigerant of the first compression mechanism (11a) and the second compression mechanism (21a). The ejector refrigeration cycle according to any one of claims 1 to 40, wherein the discharge capacity is configured to be changeable.   The first compression mechanism (11a) and the second compression mechanism (21a) are housed in the same housing and integrally formed. The ejector-type refrigeration cycle described in 1.   43. The ejector refrigeration cycle according to any one of claims 1 to 42, wherein the first compression mechanism (11a) increases the pressure of the refrigerant until it reaches a critical pressure or higher.

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