JP5018724B2 - 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 Document 1 discloses an ejector-type refrigeration cycle in which a compressor discharge refrigerant dissipates heat by exchanging heat with outdoor air using a radiator and supplies the dissipated high-pressure refrigerant to a nozzle portion of the ejector.

  Furthermore, in this ejector type refrigeration cycle, 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. At the same time, 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.

  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.

Furthermore, the recovered kinetic energy (hereinafter referred to as “recovered energy”) is converted into pressure energy at the diffuser portion of the ejector, and the pressure of the compressor suction refrigerant is increased, thereby reducing the driving power of the compressor. The coefficient of performance (COP) of the ejector refrigeration cycle is improved.
Japanese Patent No. 3322263

  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-type 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. Resulting in.

  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, COP is reduced as the flow rate of the driving flow is reduced.

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

  This will be described in detail with reference to FIG. FIG. 18 is a Mollier diagram showing the state of the refrigerant when the ejector refrigeration cycle of Patent Document 1 is operated (see FIG. 2 of Patent Document 1). Note that the solid line in FIG. 18 indicates the state of the refrigerant during normal operation, and the broken line indicates the state of the refrigerant when the above-described cycle failure occurs. Moreover, each code | symbol respond | corresponds to FIG. 2 demonstrated by embodiment mentioned later.

As is clear from FIG. 18, 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 _{18 in} FIG. ₁₈ ), the suction ability of the ejector is lowered. As a result, when the liquid-phase refrigerant is not supplied to the evaporator, the low-pressure refrigerant cannot exhibit the endothermic action in the evaporator (the white arrow Y _{18 in} FIG. ₁₈ ).

  For this reason, as shown by the broken line in FIG. 18, 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.

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

In order to achieve the above object, in the first aspect of the present invention, the first compression mechanism (11a) that compresses and discharges the refrigerant, and the heat dissipation that dissipates 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 radiator (12) and the nozzle portion (13a) that decompresses and expands the refrigerant flowing out from the radiator (12), and the jet refrigerant And an ejector (13) that boosts the mixed refrigerant of the refrigerant sucked from the refrigerant suction port (13b) at the diffuser portion (13d), and suction that evaporates the refrigerant and flows out to the refrigerant suction port (13b) side The refrigerant discharge capacity of the second compression mechanism (21a) for sucking, compressing and discharging the refrigerant on the outlet evaporator (16) and the suction side evaporator (16) is changed. Change first discharge capacity A stage (11b), a second discharge capacity changing means (21b) for changing the refrigerant discharge capacity of the second compression mechanism (21a), a first discharge capacity changing means (11b), and a second discharge capacity changing means (21b). Control means for controlling
The first discharge capacity changing means (11b) and the second discharge capacity changing means (21b) are configured to be able to change the refrigerant discharge capacity of the first compression mechanism (11a) and the second compression mechanism (21a) independently of each other. And
The control means includes a first discharge capacity changing means (11b) and a second discharge capacity changing means (so that the pressure increase amount in the first compression mechanism (11a) and the pressure increase amount in the second compression mechanism (21a) are equal. It features an ejector refrigeration cycle that controls 21b) .

  According to this, since the second compression mechanism (21a) is provided, even if the operating condition is such that the suction capacity of the ejector (13) decreases as the drive flow rate of the ejector (13) decreases. The suction capability of the ejector (13) can be assisted by the second compression mechanism (21a). As a result, the ejector refrigeration cycle can be stably operated regardless of the flow fluctuation of the driving flow.

  That is, since the second compression mechanism (21a) assists the suction capability of the ejector (13), the density of the refrigerant that flows out of the diffuser portion (13d) and is sucked into the first compression mechanism (11a) decreases. This can be suppressed. Therefore, a decrease in the flow rate of the refrigerant discharged from the first compression mechanism (11a) can be suppressed.

  As a result, even under operating conditions in which the pressure difference between the high-pressure refrigerant and the low-pressure refrigerant is likely to be reduced, a decrease in the flow rate of the drive flow can be suppressed and the ejector refrigeration cycle can be operated stably.

  In addition, as will be described later in the embodiment, the pressure of the refrigerant can be increased by the pressure increasing action of the two first and second compression mechanisms (11a, 21a) and the diffuser portion (13d) of the ejector (13). As compared with the case where the pressure of the refrigerant is increased by the machine, the driving power of the first and second compression mechanisms (11a, 21a) can be reduced to improve the COP.

  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 driving power of the first compression mechanism (11a) can be reduced, but also 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.

Accordingly, 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 (for example, about −30 ° C. to −10). When applied to COP, the COP can be improved extremely effectively.
Further, in the first aspect of the invention, as described above, the first discharge capacity changing means (11b) for changing the refrigerant discharge capacity of the first compression mechanism (11a) and the refrigerant of the second compression mechanism (21a). In adjusting the refrigerant discharge capacities of the first compression mechanism (11a) and the second compression mechanism (21a) independently by the second discharge capacity changing means (21b) that changes the discharge capacity, the first compression mechanism (11a The first discharge capacity changing means (11b) and the second discharge capacity changing means (21b) are controlled so that the pressure increase quantity at the second compression mechanism (21a) is equal.
Thus, by performing the control which makes the pressure | voltage rise amount in a 1st, 2nd compression mechanism (11a, 21a) equal, the compression efficiency of a 1st, 2nd compression mechanism (11a, 21a) is improved together. The COP of the ejector refrigeration cycle as a whole can be made substantially maximum.

  According to a second aspect of the present invention, the ejector-type refrigeration cycle according to the first aspect further includes an outflow-side gas-liquid separator (14) for separating the gas-liquid of the refrigerant that has flowed out of the diffuser section (13d). The liquid-phase refrigerant outlet of the gas-liquid separator (14) is connected to the inlet side of the suction side evaporator (16), and the gas-phase refrigerant outlet of the outflow-side gas-liquid separator (14) is the first compression mechanism ( 11a) It is connected to the suction port side.

  According to this, even when the driving flow is lowered and the suction capability of the ejector (13) is lowered, the outflow side gas-liquid separator ( The liquid phase refrigerant can be supplied from 14) to the suction-side evaporator (16). Therefore, the ejector refrigeration cycle can be operated reliably and stably.

  Furthermore, since the saturated gas-phase refrigerant can be sucked into the first compression mechanism (11a) from the gas-phase refrigerant outlet of the outflow-side gas-liquid separator (14), the case where the superheated gas-phase refrigerant is sucked can be obtained. Thus, the amount of compression work when the refrigerant is isentropically compressed in the first compression mechanism (11a) can be reduced, and the COP can be further improved.

  Further, as in the invention according to claim 3, in the ejector refrigeration cycle according to claim 2, an internal heat exchanger (for exchanging heat between the refrigerant flowing out of the radiator (12) and the low-pressure side refrigerant of the cycle) 30, 31, 32) may be provided.

  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 4, or the invention described in claim 5 of the invention. Thus, it may be a refrigerant sucked into the second compression mechanism (21a), or it may be a refrigerant inside the outflow side gas-liquid separator (14) as in the invention described in claim 6. .

  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.

  According to a seventh aspect of the present invention, in the ejector refrigeration cycle according to any one of the first to sixth aspects, the refrigerant path is arranged 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, the refrigerant flowing into the nozzle part (13a) can be depressurized by the action of the high-pressure side depressurizing means (17) until it becomes a gas-liquid two-phase refrigerant. 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.

  Further, as in the invention described in claim 8, in the ejector-type refrigeration cycle according to claim 7, the high-pressure side decompression means (17) decompresses the refrigerant by volume expansion and reduces the pressure energy of the refrigerant to the machine. It may be an expander that converts the energy into energy and outputs it. According to this, the energy efficiency as the whole ejector-type refrigeration cycle can be improved by effectively utilizing the mechanical energy output from the expander.

  In invention of Claim 9, in the ejector-type refrigerating cycle as described in any one of Claim 1 thru | or 8, a heat radiator (12) is a condensation part (12b) and a condensation part (12b) which condense a refrigerant | coolant. A gas-liquid separation unit (12c) that separates the gas-liquid of the refrigerant that has flowed out of the gas, and a supercooling unit (12d) that supercools the liquid-phase refrigerant that has flowed out of the gas-liquid separation unit (12c). Features.

  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.

  At this time, in order to decrease the enthalpy of the suction side evaporator (16) inlet side refrigerant, the first and second compression mechanisms (11a, 21a) do not increase the enthalpy of the suction refrigerant. The compression mechanism (11a, 21a) can suppress a decrease in density of the suction refrigerant. Therefore, it is possible to avoid the reduction of the discharge flow rate of the first and second compression mechanisms (11a, 21a) and to reliably improve the COP.

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

According to an eleventh aspect of the present invention, the ejector refrigeration cycle according to any one of the first to tenth aspects further includes an outflow side evaporator (61) for evaporating the refrigerant that has flowed out of the diffuser section (13d). It is characterized by.

  According to this, not only the suction side evaporator (16) but also the outflow side evaporator (61) can exhibit the refrigerating capacity. Further, in the suction side evaporator (16), the refrigerant evaporation pressure corresponds to the suction action of the injected refrigerant, and in the outflow side evaporator (61), the refrigerant evaporation 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 (61) can be made into different temperature.

As in the invention described in claim 12 , in the ejector-type refrigeration cycle according to any one of claims 1 to 11 , 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 10 of the present embodiment.

  In the ejector-type refrigeration cycle 10, the first compressor 11 sucks refrigerant, compresses and discharges it, and drives 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.

  In the ejector refrigeration cycle 10 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 refrigerant discharged from the second compressor 21 described later.

  Furthermore, a mixing unit 13c that mixes the high-speed jet refrigerant jetted from the nozzle unit 13a and the sucked refrigerant from the refrigerant suction port 13b is provided in the refrigerant flow downstream portion of the nozzle unit 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 14 is connected to the outlet side of the diffuser portion 13d.

  The accumulator 14 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 14, and the suction-side evaporator 16 is connected to the liquid-phase refrigerant outlet via a fixed throttle 15.

  The fixed throttle 15 is a low-pressure side decompression unit that further decompresses and expands the refrigerant flowing out of the accumulator 14. Specifically, an orifice or a capillary tube can be employed as the fixed throttle 15.

  The suction-side evaporator 16 heat-exchanges the low-pressure refrigerant decompressed and expanded by the fixed throttle 15 and the internal air circulated and blown by the blower fan 16a, thereby evaporating the low-pressure refrigerant and exerting an endothermic effect. Heat exchanger. Accordingly, in the present embodiment, the internal air becomes the heat exchange target fluid. The blower fan 16a is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the control device.

  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 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.

  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, 12b, 16a, 21a 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 the second electric motor 21b as the second discharge capacity change means. It also has a function as a second discharge capacity control means for controlling the operation. Of course, you may comprise a 1st discharge capability control means and a 2nd discharge capability control means with a different control apparatus.

  In addition, the control device includes a detection value of a sensor group (not shown) such as an outside air sensor that detects an outside air temperature (an outside temperature), an inside temperature sensor that detects the inside temperature, an operation switch that operates the refrigerator, and the like. Various operation signals of an operation panel (not shown) provided are input.

Next, the operation of the present embodiment in the above configuration will be described based on the Mollier diagram of FIG. When the operation switch of the operation panel is turned on, the control device operates the first and second electric motors 11b and 21b, the cooling fan 12a, and the blower fan 16a. Thereby, the 1st compressor 11 suck | inhales a refrigerant | coolant, compresses and discharges. State of the refrigerant at this time is a _2-point of FIG.

The high-temperature and high-pressure gas-phase refrigerant discharged from the first compressor 11 flows into the radiator 12, exchanges heat with the blown air (outside air) blown from the cooling fan 12a, and dissipates and condenses (see FIG. 2). a ₂ points → b ₂ points). Refrigerant radiated by the radiator 12 isentropically depressurized expansion flows into the nozzle portion 13a of the ejector 13 (b ₂ points in FIG 2 → c ₂ 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.

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 (point c ₂ → d _{2 in} FIG. 2). Point, j ₂ point → d ₂ point). 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 (d ₂ point → e ₂ point in FIG. 2).

Next, the refrigerant that has flowed out of the diffuser section 13d flows into the accumulator 14 and is separated into a gas-phase refrigerant and a liquid-phase refrigerant (e ₂ point → f ₂ point, e ₂ point → g ₂ point in FIG. ₂ ). The gas-phase refrigerant flowing out from the gas-phase refrigerant outlet of the accumulator 14 is sucked into the first compressor 11 and compressed again (point f ₂ → a _{2 in} FIG. 2).

On the other hand, the liquid-phase refrigerant that has flowed out from the outlet of the liquid-phase refrigerant of the accumulator 14 is further decompressed and expanded in an isenthalpy manner at the fixed throttle 15 to reduce its pressure (point g ₂ → point h _{2 in} FIG. 2). Decompressed and expanded refrigerant at a fixed throttle 15, and flows into the suction side evaporator 16, absorbs heat from the internal air circulated blown by the blower fan 16a to evaporate (h ₂ points in FIG 2 → i ₂ points ). Thereby, the air in a warehouse is cooled.

Then, the refrigerant flowing out from the suction side evaporator 16 is sucked into the second compressor 21 and compressed (point i ₂ → j _{2 in} FIG. 2). At this time, the control device controls the operations of the first and second electric motors 11b and 21b so that the COP of the ejector refrigeration cycle as a whole approaches a maximum. Specifically, in order to improve the compression 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 in FIG. 2).

  Since the ejector refrigeration cycle 10 of the present embodiment operates as described above, the following excellent effects can be obtained.

  Since the ejector refrigeration cycle 10 of the present embodiment includes the second compressor 21 (second compression mechanism 21a), the pressure difference between the high-pressure refrigerant and the low-pressure refrigerant is, for example, at a low outside temperature. Even if the operating condition is such that the drive flow of the ejector 13 decreases and the suction flow of the ejector 13 decreases, that is, the suction capacity of the ejector 13 is reduced by the action of the second compression mechanism 21a. Can assist.

  Then, by the action of the second compression mechanism 21a, the liquid phase refrigerant can be reliably supplied from the accumulator 14 to the suction side evaporator 16, and the endothermic action can be exhibited. Furthermore, it is possible to suppress a decrease in density of the refrigerant that flows out from the gas-phase refrigerant outlet of the accumulator 14 and is sucked into the first compressor mechanism 11a. 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 each of the first and second compression mechanisms 11a and 21a can be reduced when the pressure of the refrigerant is increased by one compression mechanism, each of the first and second compression mechanisms 11a and 21a can be reduced. 2 The compression efficiency of the 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, the COP is effectively reduced as the entire ejector refrigeration cycle 10. 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 14, 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.

(Second Embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 3, internal heat that causes the refrigerant flowing out of the radiator 12 and the low-pressure side refrigerant of the cycle to exchange heat with respect to the ejector refrigeration cycle 10 of the first embodiment. An example in which the exchanger 30 is added 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 internal heat exchanger 30 exchanges heat between the radiator 12 outlet-side refrigerant passing through the high-pressure side refrigerant flow path 30a and the first compression mechanism 11a suction refrigerant passing through the low-pressure side refrigerant flow path 30b. is there. Therefore, the low-pressure side refrigerant of the cycle in the present embodiment 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 of the first embodiment.

  Next, the operation of this embodiment will be described with reference to the Mollier diagram of FIG. In addition, the code | symbol which shows the state of the refrigerant | coolant in FIG. 4 uses the same code | symbol as the code | symbol which shows the state of the same refrigerant | coolant in FIG. 2, and has changed only the subscript. The same applies to the Mollier diagram described in the following embodiments.

When the ejector-type refrigeration cycle 10 of this embodiment is operated, the enthalpy of the first compression mechanism 11a suction-side refrigerant increases with respect to the first embodiment due to the action of the internal heat exchanger 30 (f _{4 in} FIG. 4). point → f _'4 points), the enthalpy of the refrigerant flowing out of the radiator 12 decreases (b ₄ points of FIG. 4 → b' ₄ points). Other operations are the same as those in the first embodiment.

  Thereby, since the dryness of the injection refrigerant | coolant injected from the nozzle 13a can be reduced and the flow velocity of an injection refrigerant | coolant can be reduced, the refrigerant | coolant pressure which flows out from the diffuser part 13d can be reduced. Therefore, the enthalpy of the refrigerant in the accumulator 14 can be reduced, and the enthalpy of the liquid phase refrigerant flowing from the accumulator 14 to the suction side evaporator 16 can also be reduced.

  Therefore, not only can the same effect as in the first embodiment be obtained, but also the enthalpy difference between the enthalpy of the inlet side refrigerant and the enthalpy of the outlet side refrigerant of the suction side evaporator 16 can be increased, and the ejector refrigeration cycle The refrigerating capacity that can be exhibited by 10 can be increased. As a result, COP can be further improved.

(Third embodiment)
In the present embodiment, an example in which an internal heat exchanger 31 is added to the ejector refrigeration cycle 10 of the first embodiment will be described as shown in the overall configuration diagram of FIG. The basic configuration of the internal heat exchanger 31 is the same as that of the internal heat exchanger 30 of the second embodiment.

  Specifically, the internal heat exchanger 31 exchanges heat between the radiator 12 outlet-side refrigerant passing through the high-pressure side refrigerant flow path 31a and the second compression mechanism 21a suction refrigerant passing through the low-pressure side refrigerant flow path 31b. Is to do. Therefore, the low-pressure side refrigerant in the cycle of the present embodiment is a refrigerant sucked into the second compression mechanism 21a. Other configurations are the same as those of the first embodiment.

Next, the operation of this embodiment will be described with reference to the Mollier diagram of FIG. When the ejector-type refrigeration cycle 10 of the present embodiment is operated, the enthalpy of the second compression mechanism 21a suction-side refrigerant increases with respect to the first embodiment due to the action of the internal heat exchanger 31 (i _{6 in} FIG. 6). point → i _'6 points), the enthalpy of the refrigerant flowing out of the radiator 12 decreases (b ₆ points in FIG. 6 → b' ₆ points). Other operations are the same as those in the first embodiment.

  Accordingly, in the ejector refrigeration cycle 10 of the present embodiment, the enthalpy of the liquid-phase refrigerant flowing from the accumulator 14 to the suction side evaporator 16 can be reduced as in the second embodiment.

  By the way, in the internal heat exchanger 31 of this embodiment, heat is exchanged between the radiator 12 outlet side refrigerant and the second compression mechanism 21a suction side refrigerant. For this reason, the refrigerant flowing into the nozzle portion 13 a of the ejector 13 is cooled by the internal heat exchanger 31, and the refrigerant sucked into the second compression mechanism 21 a is heated by the internal heat exchanger 31.

  In other words, after the heat exchange between the jet refrigerant injected from the nozzle portion 13a and the suction refrigerant sucked from the refrigerant suction port 13b is performed on the upstream side of the nozzle portion 13a and the second compressor 21, respectively, the mixing portion 13c. Will be mixed again. Therefore, the enthalpy of the mixed refrigerant is less likely to decrease than when the internal heat exchanger 31 is not provided (for example, the first embodiment), and there is a concern that the enthalpy of the refrigerant flowing into the accumulator 14 is also difficult to decrease. .

  On the other hand, in the ejector refrigeration cycle 10 of the present embodiment, the flow rate of the suction refrigerant is smaller than the flow rate of the injection refrigerant, so that the flow rate of the injection refrigerant reduces the flow rate of the refrigerant flowing out of the diffuser portion 13d. The pressure can be reduced sufficiently. Therefore, the enthalpy of the refrigerant flowing into the accumulator 14 can be reduced.

  As a result, not only can the same effect as in the first embodiment be obtained, but also the enthalpy difference between the enthalpy of the inlet-side refrigerant and the enthalpy of the outlet-side refrigerant of the suction-side evaporator 16 can be expanded as in the second embodiment. Thus, the refrigeration capacity that can be exhibited by the ejector refrigeration cycle 10 can be increased.

(Fourth embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 7, with respect to the first embodiment, the refrigerant passage is arranged from the radiator 12 outlet side to the nozzle portion 13a upstream side and passes through the refrigerant passage. An example will be described in which a temperature type expansion valve 17 is added as a high pressure side pressure reducing means for decompressing and expanding the high pressure refrigerant.

  This temperature type expansion valve 17 has a temperature sensing part 17a disposed in the refrigerant passage at the outlet side of the suction side evaporator 16, and based on the temperature and pressure of the refrigerant at the outlet side of the suction side evaporator 16, This is a variable throttle mechanism that detects the degree of superheat of the refrigerant on the outlet side of the evaporator 16 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. Other configurations are the same as those of the first embodiment.

Next, the operation of this embodiment will be described with reference to the Mollier diagram of FIG. When the ejector-type refrigeration cycle 10 of the present embodiment is operated, the refrigerant radiated by the radiator 12 flows into the temperature type expansion valve 17 and is decompressed and expanded in an enthalpy manner to a gas-liquid two-phase state (see FIG. 8 b ₈ points-> b ' ₈ points). At this time, the opening degree of the temperature type expansion valve 17 is adjusted so that the superheat degree of the refrigerant on the outlet side of the suction side evaporator 16 becomes a predetermined value set in advance.

The intermediate-pressure refrigerant decompressed and expanded by the temperature type expansion valve 17 is isentropically depressurized by the nozzle portion 13a of the ejector 13 and is sucked from the refrigerant suction port 13b, as in the first embodiment. It is mixed and flows into the accumulator 14. Gas-phase refrigerant to gas-liquid separation in the accumulator 14 is compressed again is sucked into the first compressor 11 (c ₈ points in Fig. 8 → d ₈ points → e ₈ points → f ₈ points → a _8-point) .

On the other hand, the liquid-phase refrigerant separated by the accumulator 14 is decompressed in an enthalpy manner by the fixed throttle 15, absorbs heat from the blown air inside the cabinet by the suction side evaporator 16, and is sucked into the second compressor 21. . Moreover, the refrigerant discharged from the second compressor 21 is sucked from the refrigerant suction port 13b of the ejector 13 (g ₈ points in Fig. 8 → h ₈ points → i ₈ points → j ₈ points → d ₈ points).

  Therefore, in the ejector type refrigeration cycle 10 of the present embodiment, not only can the same effect as in the first embodiment be obtained, but also the temperature type expansion valve 17 that is a variable throttle mechanism is employed as the high pressure side pressure reducing means. The flow rate of the refrigerant flowing into the nozzle portion 13a of the ejector 13 can be changed 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.

  Furthermore, since the valve opening degree of the temperature type expansion valve 17 is adjusted so that the superheat degree of the suction side evaporator 16 outlet side refrigerant becomes a predetermined value set in advance, the problem of liquid compression of the second compressor 21 Can be avoided.

Further, in the present embodiment, the refrigerant (point b ₈ ′ in FIG. 8) decompressed and expanded by the temperature type expansion valve 17 is in a gas-liquid two-phase state, so that the gas-liquid two-phase state is supplied to the nozzle portion 13 a of the ejector 13. The refrigerant can be introduced.

  Thereby, with respect to the case where the liquid phase refrigerant is caused to flow into the nozzle portion 13a, boiling of the refrigerant in the nozzle portion 13a can be promoted, and the nozzle efficiency can be improved. As a result, the amount of energy recovered by the ejector 13 can be increased and the amount of pressure increase in the diffuser portion 13d can be increased, so that the COP can be further improved.

  Furthermore, since the refrigerant passage area of the nozzle 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.

(Fifth embodiment)
In the present embodiment, an example in which an internal heat exchanger 32 is added to the ejector refrigeration cycle 10 of the fourth embodiment will be described as shown in the overall configuration diagram of FIG. The internal heat exchanger 32 exchanges heat between the radiator 12 outlet-side refrigerant and the gas-phase refrigerant in the accumulator 14. That is, the low-pressure side refrigerant of the cycle in the present embodiment is a gas-phase refrigerant in the accumulator 14.

  Specifically, the internal heat exchanger 32 passes the high-pressure pipe 32a through which the refrigerant on the outlet side of the radiator 12 flows through the space in which the gas-phase refrigerant in the accumulator 14 is stored (the upper space in the accumulator 14). It is configured. Therefore, the internal heat exchanger 32 of the present embodiment is configured integrally with the accumulator 14.

  As in this embodiment, the high-pressure pipe 32a of the internal heat exchanger 32 is configured to pass through the upper space in the accumulator 14, so that the liquid phase refrigerant in the accumulator 14 is stored (in the accumulator 14). ), The unnecessary boiling of the liquid refrigerant in the accumulator 14 can be suppressed.

  Of course, when this boiling does not become a problem, the high-pressure pipe 32a of the internal heat exchanger 32 may be configured to pass through a space in which the liquid-phase refrigerant in the accumulator 14 is stored. Other configurations are the same as those of the fourth embodiment.

Next, the operation of this embodiment will be described with reference to the Mollier diagram of FIG. Operating the ejector refrigeration cycle 10 of this embodiment, by the action of the internal heat exchanger 32, the enthalpy of the first compression mechanism 11a suction side refrigerant is increased (f ₁₀ points in FIG. 10 → f _'10 points), enthalpy of the refrigerant flowing from the radiator 12 is reduced (b ₁₀ points in FIG. 10 → b _'10 points).

Furthermore, the refrigerant flowing out from the high-pressure pipe 32a of the internal heat exchanger 32 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, as in the fourth embodiment ( B ′ ₁₀ points → b ″ ₁₀ points in FIG. 10) Other operations are the same as in the first embodiment.

  Therefore, 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 by the action of the internal heat exchanger 32 as in the second embodiment. Furthermore, the nozzle efficiency in the nozzle portion 13a of the ejector 13 can be improved by the action of the temperature type expansion valve 17 as in the fourth embodiment.

  As a result, not only can the effect similar to that of the first embodiment be obtained, but also the refrigeration capacity that can be exhibited by the ejector refrigeration cycle 10 can be increased as in the second embodiment. Similarly to the above, since the amount of pressure increase in the diffuser portion 13d can be increased, the COP can be further improved.

(Sixth embodiment)
In the present embodiment, an example in which the configuration of the radiator 12 is changed with respect to the ejector refrigeration cycle 10 of the fourth embodiment as illustrated in the overall configuration diagram of FIG. 11 will be described.

  Specifically, the radiator 12 of the present embodiment includes a condensing unit 12b that condenses the refrigerant, a gas-liquid separation unit 12c (receiver unit) that separates the gas-liquid of the refrigerant that has flowed out of the condensing unit 12b, and a gas-liquid separation. This is configured as a so-called subcool condenser having a supercooling part 12d for supercooling the liquid-phase refrigerant flowing out from the part 12c. Other configurations are the same as those of the fourth embodiment.

Next, the operation of this embodiment will be described with reference to the Mollier diagram of FIG. Operating the ejector refrigeration cycle 10 of the present embodiment, the refrigerant condensed in the condensation portion 12b of the radiator 12 is gas-liquid separated by the gas-liquid separator 12c (b ₁₂ points in FIG. 12). Further, the separated saturated liquid refrigerant is supercooled of at supercooling part 12d (b ₁₂ points in FIG. 12 → b _'12 points). Other operations are the same as those in the fourth embodiment.

  Thereby, since the dryness of the injection refrigerant | coolant injected from the nozzle 13a can be reduced and the flow velocity of an injection refrigerant | coolant can be reduced, the refrigerant | coolant pressure which flows out from the diffuser part 13d can be reduced. Therefore, the enthalpy of the refrigerant in the accumulator 14 can be reduced, and the enthalpy of the liquid phase refrigerant flowing from the accumulator 14 to the suction side evaporator 16 can also be reduced.

  As a result, 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, and the refrigeration capacity that can be exhibited by the ejector refrigeration cycle 10 can be increased.

Further, at this time, for example, as in the case of using the internal heat exchanger 31 (see FIGS. 5 and 6) of the third embodiment, the enthalpy of the second compression mechanism 21a suction-side refrigerant (cycle low-pressure side refrigerant) is reduced. It is not increased unnecessarily (i ₁₂ points in FIG. 12). Therefore, it is possible to reduce the refrigerant evaporation pressure (refrigerant evaporation temperature) in the suction-side evaporator 16 with respect to the third embodiment by suppressing the density of the refrigerant sucked by the second compression mechanism 21a. .

Further, the refrigerant flowing out from the supercooling part 12d of the radiator 12 is decompressed and expanded by the temperature type expansion valve 17 until it becomes a gas-liquid two-phase state (b ′ ₁₂ point → b ″ ₁₂ point in FIG. 12). Therefore, similarly to the fourth embodiment, the nozzle efficiency of the ejector 13 can be improved.

  As a result, not only the same effects as in the first embodiment can be obtained, but also the refrigeration capacity that can be exhibited by the ejector refrigeration cycle 10 is increased. Further, as in the fourth embodiment, the amount of pressure increase in the diffuser portion 13d can be increased. Since it can be increased, COP can be further improved.

(Seventh embodiment)
In the present embodiment, as shown in the overall configuration diagram of FIG. 13 and the Mollier diagram of FIG. 14, the downstream side of the diffuser portion 13d of the ejector 13 with respect to the ejector refrigeration cycle 10 of the first embodiment, An example in which the outflow side evaporator 61 is disposed upstream of the accumulator 14 will be described.

  The basic configuration of the outflow side evaporator 61 is the same as that of the suction side evaporator 16. Further, the outflow side evaporator 61 exchanges heat between the refrigerant flowing out from the ejector 13 and the blown air blown from the blower fan 61a, thereby evaporating the refrigerant flowing out of the ejector 13 and exerting an endothermic effect. It is a vessel.

  Accordingly, in the present embodiment, the blown air blown from the blower fan 61a is also the heat exchange target fluid. The blower fan 61a is an electric blower in which the rotation speed (amount of blown air) is controlled by a control voltage output from the control device. Other configurations are the same as those of the first embodiment.

When the ejector-type refrigeration cycle of this embodiment is operated, the same effect as that of the first embodiment can be obtained, and in the outflow side evaporator 61, as shown in the Mollier diagram of FIG. In the process from the e ₁₄ point to the e ′ ₁₄ point, the refrigerant can be evaporated to exert an endothermic effect. Thereby, the blowing air from the blowing fan 61a can also be cooled.

  At this time, in the outflow side evaporator 61, the refrigerant evaporates at a temperature higher than the refrigerant evaporation temperature in the suction side evaporator 16. That is, in the suction side evaporator 16 and the outflow side evaporator 61, the refrigerant evaporates in different temperature zones. Thereby, in this embodiment, while being able to acquire the effect similar to 1st Embodiment, the air in the refrigerator in a refrigerator which preserve | saves food, a drink, etc. at the low temperature of 0 to 10 degreeC with the ventilation fan 61a, for example. Can also be cooled.

  Of course, the outflow evaporator 61 may be added to the ejector refrigeration cycle 10 of the second to sixth embodiments.

(Eighth embodiment)
In this embodiment, as shown in the overall configuration diagram of FIG. 15, a bypass passage 25, an on-off valve 26, a check valve 27, and a gas-liquid separator 28 are added to the ejector refrigeration cycle 10 of the first embodiment. An example will be described.

  The bypass passage 25 is a refrigerant flow path that guides the high-pressure refrigerant discharged from the first compression mechanism 11a to the suction side evaporator 16 by bypassing the radiator 12, and the first compression mechanism 11a, the radiator 12, and the like. And a refrigerant pipe connecting the fixed throttle 15 and the suction side evaporator 16. The opening / closing valve 26 is an opening / closing means for opening / closing the bypass passage 25 and is an electromagnetic valve whose opening / closing operation is controlled by a control signal output from the control device.

  The check valve 27 is disposed between the fixed throttle 15 and the connection portion of the bypass passage 25 and allows only the refrigerant to flow from the fixed throttle 15 side to the suction side evaporator 16 side. That is, the refrigerant flowing out from the bypass passage 25 to the suction side evaporator 16 side is prohibited from flowing to the accumulator 14 side (fixed throttle 15 side). The gas-liquid separator 28 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 10 of the present embodiment is operated, when the control device closes the on-off valve 26, the control device operates in the same manner as in the first embodiment, so that the same effect as in the first embodiment can be obtained. it can.

  Further, with respect to the ejector refrigeration cycle 10 of the first embodiment, a bypass passage 25 that bypasses the radiator 12 and guides the high-pressure refrigerant discharged from the first compression mechanism 11a to the suction side evaporator 16, and bypass Since opening / closing means 26 for opening and closing the passage 25 and a check valve 27 for prohibiting the refrigerant flowing out of the bypass passage 25 from flowing to the outflow side gas-liquid separator 14 side are provided, it is attached to the suction side evaporator 16. When frost occurs, 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 via the bypass passage 25 and is removed. Can be frosted.

  In addition, a suction-side gas-liquid separator 28 that is disposed between the suction-side evaporator 16 and the second compression mechanism 21a and separates the gas-liquid refrigerant is provided, and the gas-phase refrigerant outlet of the suction-side gas-liquid separator 28 is Since the second compression mechanism 21a is connected to the suction port side, the vapor phase separated by the suction-side gas-liquid separator 28 even if the high-temperature refrigerant discharged from the first compression mechanism 11a is condensed during defrosting. Only the refrigerant can be supplied to the second compression mechanism 21a, and the problem of liquid compression of the second compression mechanism 21a can be avoided.

(Ninth embodiment)
Next, a ninth embodiment of the present invention will be described with reference to FIG. In this embodiment, the ejector refrigeration cycle of the present invention is applied to an air conditioner for indoor air conditioning. FIG. 16 is an overall configuration diagram of the ejector refrigeration cycle 40 of the present embodiment.

  The ejector refrigeration cycle 40 is configured to be switchable between a cooling operation mode for cooling indoor blown air that is a heat exchange target fluid and a heating operation mode for heating indoor blown air. In addition, the solid line arrow in FIG. 16 shows the flow of the refrigerant in the cooling operation mode, and the broken line arrow shows the flow of the refrigerant in the heating operation mode.

  In the ejector refrigeration cycle 40 of the present embodiment, a first electric four-way valve 41 is connected to the refrigerant discharge side of the first compression mechanism 11a. The first electric four-way valve 41 is a refrigerant flow switching means whose operation is controlled by a control signal output from the control device.

  Specifically, the first electric four-way valve 41 is provided between the discharge port side of the first compressor 11 and the outdoor heat exchanger 42, the liquid phase refrigerant outlet side (fixed throttle 15 side) of the accumulator 14, and the use side heat. The refrigerant flow path (the circuit indicated by the solid line arrow in FIG. 16) that connects the exchanger 44 at the same time, the first compressor 11 discharge side and the use side heat exchanger 44, and the liquid phase refrigerant of the accumulator 14 The refrigerant flow path (circuit indicated by the broken line arrow in FIG. 16) that connects the outlet side (fixed throttle 15 side) and the outdoor heat exchanger 42 at the same time is switched.

  An outdoor heat exchanger 42 is connected to the discharge side of the first compressor 11 in the cooling operation mode via the first electric four-way valve 41 as in the refrigerant flow path indicated by the solid line arrow in FIG. . The outdoor heat exchanger 42 is a heat exchanger that exchanges heat between the refrigerant passing through the inside and the outdoor air blown by the blower fan 42a. The blower fan 42a 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.

  Further, a second electric four-way valve 43 is connected to the outlet side of the outdoor heat exchanger 42 in the cooling operation mode. The second electric four-way valve 43 is refrigerant flow switching means whose operation is controlled by a control signal output from the control device, and the basic configuration is the same as that of the first electric four-way valve 41. is there.

  Specifically, the second electric four-way valve 43 is provided between the outdoor heat exchanger 42 and the nozzle part 13a inlet side of the ejector 13 and between the use side heat exchanger 44 and the second compressor 21 inlet side. Between the refrigerant flow path (circuit shown by the solid line arrow in FIG. 16), the outdoor heat exchanger 42 and the second compressor 21 suction side, and the use side heat exchanger 44 and the nozzle portion 13a of the ejector 13. The refrigerant flow path (circuit indicated by the broken line arrow in FIG. 16) that connects the inlet side at the same time is switched.

  The use-side heat exchanger 44 is a heat exchanger that exchanges heat between the refrigerant passing through the inside and the indoor blown air that is the heat exchange target fluid blown by the blower fan 44a. The blower fan 44a 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 fixed throttle 15 of the present embodiment is disposed between the liquid refrigerant outlet side of the accumulator 14 and the first electric four-way valve 41. Other configurations are the same as those of the first embodiment.

  Next, the operation of this embodiment in the above configuration will be described. In the ejector type refrigeration cycle 40 of the present embodiment, it is possible to switch between a cooling operation mode (cooling operation mode) for cooling indoor blown air and a heating operation mode (heating operation mode) for heating indoor blown air.

a. Cooling operation mode The cooling operation mode is executed when the cooling operation mode is selected by the operation switch of the operation panel.

  In the cooling operation mode, the control device operates the first and second electric motors 11b and 21b and the blower fans 42a and 44a, and between the discharge port side of the first compressor 11 and the outdoor heat exchanger 42 and the accumulator 14. The first electric four-way valve 41 is switched so as to connect the liquid-phase refrigerant outlet side and the use-side heat exchanger 44 at the same time, and between the outdoor heat exchanger 42 and the nozzle portion 13a inlet side of the ejector 13 and The second electric four-way valve 43 is switched so as to simultaneously connect the use side heat exchanger 44 and the second compressor 21 suction side.

  Thereby, as shown by the solid line arrow in FIG. 16, the first compressor 11 (→ first electric four-way valve 41) → outdoor heat exchanger 42 (→ second electric four-way valve 43) → nozzle portion of the ejector 13. The refrigerant circulates in the order of 13a → the gas phase refrigerant outlet of the accumulator 14 → the first compressor 11, and the liquid phase refrigerant outlet of the accumulator 14 → the fixed throttle 15 (→ the first electric four-way valve 41) → the use side heat exchanger. 44 (→ second electric four-way valve 43) → second compressor 21 → refrigerant suction port 13b of the ejector 13 → accumulator 14 in the order of circulation of the refrigerant.

  Accordingly, the refrigerant compressed by the first compression mechanism 11 a is cooled by exchanging heat with the outside air blown by the blower fan 42 a by the outdoor heat exchanger 42, and isentropically formed by the nozzle portion 13 a of the ejector 13. Injected after decompression. Due to the suction action of the jet refrigerant, the refrigerant discharged from the second compression mechanism 21a is sucked from the refrigerant suction port 13b.

  Further, the refrigerant injected from the nozzle portion 13a and the suction refrigerant sucked from the refrigerant suction port 13b are mixed by the mixing portion 13c of the ejector 13, and the pressure is increased by the diffuser portion 13d. The refrigerant flowing out from the diffuser portion 13d is gas-liquid separated by the accumulator 14, and the gas phase refrigerant flowing out from the gas phase refrigerant outlet of the accumulator 14 is sucked into the first compression mechanism 11a and compressed again.

  On the other hand, the liquid-phase refrigerant that has flowed out from the liquid-phase refrigerant outlet of the accumulator 14 is further decompressed and expanded in an isenthalpy manner by the fixed throttle 15, and is sent to the use side heat exchanger 44 via the first electric four-way valve 41. It flows in, absorbs heat from the indoor air blown by the blower fan 44a, and evaporates. Thereby, indoor ventilation air is cooled.

  And the refrigerant | coolant which flowed out from the use side heat exchanger 44 is suck | inhaled by the 2nd compression mechanism 21a, and is compressed. At this time, similarly to the first embodiment, the control device controls the operations of the first and second electric motors 11b and 21b so that the COP as the entire ejector-type refrigeration cycle approaches the maximum.

  That is, in the cooling operation mode of the present embodiment, the refrigerant discharged from the first compression mechanism 11a is radiated by the outdoor heat exchanger 42 and switched to the refrigerant flow path for evaporating the refrigerant by the use side heat exchanger 44. ing.

  More specifically, the outdoor heat exchanger 42 is caused to function in the same manner as the radiator 12 of the first embodiment, and the refrigerant radiated by the outdoor heat exchanger 42 is caused to flow into the nozzle portion 13a of the ejector 13 and used. The side heat exchanger 44 is caused to function in the same manner as the suction side evaporator 16 of the first embodiment, and the liquid-phase refrigerant separated by the accumulator 14 is evaporated by the use side heat exchanger 44 and sucked into the second compression mechanism 21a. The refrigerant flow path is changed to flow out to the side.

  Therefore, in the cooling operation mode of the present embodiment, the indoor blown air can be cooled, and at this time, similarly to the first embodiment, the flow rate of the drive flow of the ejector 13 is suppressed by the action of the second compression mechanism 21a. The ejector refrigeration cycle can be operated stably and the COP can be improved.

b. Heating operation mode The heating operation mode is executed when the heating operation mode is selected by the operation switch of the operation panel.

  In the heating operation mode, the control device operates the first and second electric motors 11b and 21b, and the blower fans 42a and 44a, and between the discharge port side of the first compressor 11 and the use side heat exchanger 44 and the accumulator. 14, the first electric four-way valve 41 is switched so as to simultaneously connect the liquid-phase refrigerant outlet side and the outdoor heat exchanger 42, and between the outdoor heat exchanger 42 and the second compressor 21 suction side and The second electric four-way valve 43 is switched so that the use side heat exchanger 44 and the nozzle portion 13a inlet side of the ejector 13 are connected simultaneously.

  Thereby, as shown by the broken line arrow in FIG. 16, the first compressor 11 (→ the first electric four-way valve 41) → the use side heat exchanger 44 (→ the second electric four-way valve 43) → the nozzle of the ejector 13. The refrigerant circulates in the order of the section 13a → the gas-phase refrigerant outlet of the accumulator 14 → the first compressor 11 and the liquid-phase refrigerant outlet of the accumulator 14 → the fixed throttle 15 (→ first electric four-way valve 41) → outdoor heat exchanger. A cycle in which the refrigerant circulates in the order of 42 (→ second electric four-way valve 43) → second compressor 21 → refrigerant suction port 13b of the ejector 13 → accumulator 14 is configured.

  Therefore, the refrigerant compressed by the first compression mechanism 11a exchanges heat with the indoor air blown by the blower fan 44a in the use side heat exchanger 44 and dissipates heat. Thereby, indoor blowing air is heated. The refrigerant radiated and cooled by the use side heat exchanger 44 is decompressed and expanded in an isentropic manner at the nozzle portion 13a of the ejector 13 and is injected. Due to the suction action of the jet refrigerant, the refrigerant discharged from the second compression mechanism 21a is sucked from the refrigerant suction port 13b.

  Further, the refrigerant injected from the nozzle portion 13a and the suction refrigerant sucked from the refrigerant suction port 13b are mixed by the mixing portion 13c of the ejector 13, and the pressure is increased by the diffuser portion 13d. The refrigerant flowing out from the diffuser portion 13d is gas-liquid separated by the accumulator 14, and the gas phase refrigerant flowing out from the gas phase refrigerant outlet is sucked into the first compression mechanism 11a and compressed again.

  On the other hand, the liquid-phase refrigerant that has flowed out from the liquid-phase refrigerant outlet of the accumulator 14 is further decompressed and expanded isoenthalpically by the fixed throttle 15 and flows into the outdoor heat exchanger 42 via the first electric four-way valve 41. Then, it absorbs heat from the outside air blown by the blower fan 42a and evaporates.

  And the refrigerant | coolant which flowed out from the outdoor heat exchanger 42 is suck | inhaled by the 2nd compression mechanism 21a, and is discharged to the refrigerant | coolant suction port 14b side. At this time, similarly to the first embodiment, the control device controls the operations of the first and second electric motors 11b and 21b so that the COP as the entire ejector-type refrigeration cycle approaches the maximum.

  That is, in the heating operation mode of the present embodiment, the refrigerant discharged from the first compressor 11 is radiated by the use side heat exchanger 44 and switched to the refrigerant flow path for evaporating the refrigerant by the outdoor heat exchanger 42. ing.

  More specifically, the use side heat exchanger 44 is caused to function in the same manner as the radiator 12 of the first embodiment, and the refrigerant radiated by the use side heat exchanger 44 is caused to flow into the nozzle portion 13a of the ejector 13. The outdoor heat exchanger 42 is caused to function in the same manner as the suction-side evaporator 16 of the first embodiment, and the liquid refrigerant separated by the accumulator 14 is evaporated by the outdoor heat exchanger 42 to be sucked into the second compression mechanism 21a. The refrigerant flow path is changed to flow out to the side.

  Therefore, in the heating operation mode of the present embodiment, the indoor blown air can be heated, and at this time, as in the first embodiment, the flow rate of the drive flow of the ejector 13 is suppressed by the action of the second compressor 21, The ejector refrigeration cycle can be operated stably and the COP can be improved.

  More specifically, in the present embodiment, the refrigerant flow switching means 41 and 43 for switching the refrigerant flow path in the cooling operation mode for cooling the fluid to be heat exchanged and the refrigerant flow path in the heating operation mode for heating the fluid to be heat exchanged. In at least one of the cooling operation mode and the heating operation mode, the high-speed injection refrigerant that is injected from the nozzle portion 13a that decompresses and expands the refrigerant that has radiated heat in the use side heat exchanger 44 or the outdoor heat exchanger 42 The ejector 13 that sucks the refrigerant from the refrigerant suction port 13b by the flow and pressurizes the mixed refrigerant of the injected refrigerant and the suction refrigerant sucked from the refrigerant suction port 13b at the diffuser portion 13d, and the cooling operation mode and the heating operation. In at least one of the operation modes, the refrigerant evaporated in the use side heat exchanger 44 or the outdoor heat exchanger 42 is sucked. And a second compression mechanism 21a that compresses and discharges the refrigerant to the refrigerant suction port 13b side. Further, in the cooling operation mode, the refrigerant flow switching means 41 and 43 are configured to discharge the refrigerant discharged from the first compression mechanism 11a. In the heating operation mode, the refrigerant discharged from the first compression mechanism 11a is used as the utilization side heat exchanger while the outdoor heat exchanger 42 radiates heat and the utilization side heat exchanger 44 switches to the refrigerant flow path for evaporating the refrigerant. 44, and the outdoor heat exchanger 42 switches to the refrigerant flow path for evaporating the refrigerant. Accordingly, the flow rate of the drive flow of the ejector 13 is reduced in at least one of the cooling operation mode and the heating operation mode. Even if the suction capability of the ejector 13 is reduced, the suction capability of the ejector 13 can be assisted by the second compression mechanism 21a.

  Specifically, an outflow-side gas-liquid separator 14 that separates the gas-liquid of the refrigerant flowing out from the diffuser portion 13d is provided, and the gas-phase refrigerant outlet of the outflow-side gas-liquid separator 14 is an inlet of the first compression mechanism 11a. In the cooling operation mode, the refrigerant flow switching means 41 and 43 allow the refrigerant radiated by the outdoor heat exchanger 42 to flow into the nozzle portion 13a and be separated by the outflow side gas-liquid separator 14. In the heating operation mode, the refrigerant that has radiated heat in the utilization side heat exchanger 44 is switched to a refrigerant flow path that evaporates the liquid phase refrigerant that has been evaporated in the utilization side heat exchanger 44 and flows out to the suction side of the second compression mechanism 21a. Since the liquid phase refrigerant separated by the outflow side gas-liquid separator 14 is evaporated by the outdoor heat exchanger 42 and switched to the refrigerant flow path that flows out to the suction side of the second compression mechanism 21a. Cooling operation mode Even if the suction capacity of the ejector 13 is reduced due to a decrease in the flow rate of the drive flow of the ejector 13 in any of the operation modes, the second compression mechanism 21a, the suction capacity of the ejector 13 can be assisted. it can.

  As a result, the ejector refrigeration cycle can be stably operated in any of the cooling operation mode and the heating operation mode regardless of the flow rate fluctuation of the drive flow.

(10th Embodiment)
In the present embodiment, as shown in FIG. 17, the second electric four-way valve 43 of the ejector refrigeration cycle 40 of the ninth embodiment is abolished, and the on-off valve 51 and the electric three-way valve 52 serve as refrigerant flow switching means. An example in which the second fixed throttle 53 is provided as a decompression means for decompressing and expanding the refrigerant in the heating operation mode will be described.

  FIG. 17 is an overall configuration diagram of the ejector refrigeration cycle 40 of the present embodiment. The solid line arrow in FIG. 17 indicates the flow of the refrigerant in the cooling operation mode, and the broken line arrow indicates the refrigerant flow in the heating operation mode. The flow is shown. In the present embodiment, the fixed diaphragm 15 is expressed as the first fixed diaphragm 15 in order to clarify the difference from the second fixed diaphragm 53.

  In the ejector type refrigeration cycle 40 of the present embodiment, the three-way joint 54 having three refrigerant inflow / outflow ports on the outlet side of the outdoor heat exchanger 42 in the cooling operation mode, as in the refrigerant flow path indicated by the solid line arrow in FIG. One inlet / outlet is connected. The three-way joint 54 may be configured by joining pipes having different pipe diameters or equivalent, or by providing a plurality of refrigerant passages having different passage diameters or equivalent to a metal block or a resin block. May be.

  Further, the inlet side of the nozzle portion 13 of the ejector 13 is connected to the other inlet / outlet of the three-way joint 54 via the opening / closing valve 51. The on-off valve 51 is an electromagnetic valve whose operation is controlled by a control signal output from the control device. Furthermore, an electric three-way valve 52 is connected to another inflow / outlet of the three-way joint 54 via a second fixed throttle 53.

  The basic configuration of the second fixed aperture 53 is the same as that of the first fixed aperture 15. Further, the operation of the electric three-way valve 52 is controlled by a control signal output from the control device, and the refrigerant flow path connecting between the use side heat exchanger 44 and the second compressor 21 suction side. (A circuit indicated by a solid line arrow in FIG. 17) and a refrigerant flow path (a circuit indicated by a broken line arrow in FIG. 17) connecting the use side heat exchanger 44 and the second fixed throttle 53 are switched.

  Therefore, in the present embodiment, the on / off valve 51 and the electric three-way valve 52 together with the first electric four-way valve 41 constitute a refrigerant flow path switching means. Other configurations are the same as those of the ninth embodiment.

  Next, the operation of this embodiment in the above configuration will be described. In the ejector type refrigeration cycle 40 of the present embodiment, it is possible to switch between a cooling operation mode (cooling operation mode) for cooling indoor blown air and a heating operation mode (heating operation mode) for heating indoor blown air.

a. Cooling operation mode The cooling operation mode is executed when the cooling operation mode is selected by the operation switch of the operation panel.

  In the cooling operation mode, the control device operates the first and second electric motors 11b and 21b and the blower fans 42a and 44a, and between the discharge port side of the first compressor 11 and the outdoor heat exchanger 42 and the accumulator 14. The first electric four-way valve 41 is switched so as to connect the liquid-phase refrigerant outlet side and the use-side heat exchanger 44 at the same time, and between the use-side heat exchanger 44 and the second compressor 21 suction side. The electric three-way valve 52 is switched so as to be connected, and the on-off valve 51 is opened.

  As a result, as indicated by the solid line arrow in FIG. 17, the first compressor 11 (→ first electric four-way valve 41) → outdoor heat exchanger 42 (→ three-way joint 54 → open / close valve 51) → nozzle portion of the ejector 13 The refrigerant circulates in the order of 13a → the gas phase refrigerant outlet of the accumulator 14 → the first compressor 11 and the liquid phase refrigerant outlet of the accumulator 14 → the first fixed throttle 15 (→ the first electric four-way valve 41) → the use side heat. A cycle is formed in which the refrigerant circulates in the order of the exchanger 44 (→ electric three-way valve 52) → second compressor 21 → refrigerant suction port 13b of the ejector 13 → accumulator 14.

  Therefore, in the cooling operation mode of the present embodiment, the refrigerant discharged from the first compression mechanism 11a is radiated by the outdoor heat exchanger 42 and the use-side heat exchanger is provided, as in the cooling operation mode of the ninth embodiment. At 44, the refrigerant flow path for evaporating the refrigerant is switched.

  More specifically, the outdoor heat exchanger 42 is caused to function in the same manner as the radiator 12 of the first embodiment, and the refrigerant radiated by the outdoor heat exchanger 42 is caused to flow into the nozzle portion 13a of the ejector 13 and used. The side heat exchanger 44 is caused to function in the same manner as the suction side evaporator 16 of the first embodiment, and the liquid-phase refrigerant separated by the accumulator 14 is evaporated by the use side heat exchanger 44 and sucked into the second compression mechanism 21a. The refrigerant flow path is changed to flow out to the side.

  Thereby, in the air_conditionaing | cooling operation mode of this embodiment, indoor blowing air can be cooled similarly to 9th Embodiment.

b. Heating operation mode The heating operation mode is executed when the heating operation mode is selected by the operation switch of the operation panel.

  In the heating operation mode, the control device operates the first and second electric motors 11b and 21b, and the blower fans 42a and 44a, and between the discharge port side of the first compressor 11 and the use side heat exchanger 44 and the accumulator. The first electric four-way valve 41 is switched so that the liquid-phase refrigerant outlet side of the fourteenth and the outdoor heat exchanger 42 are simultaneously connected, and the use-side heat exchanger 44 and the second fixed throttle 53 are connected. The electric three-way valve 52 is switched and the on-off valve 51 is opened.

  Thereby, as shown by the broken line arrow in FIG. 17, the first compressor 11 (→ first electric four-way valve 41) → the use side heat exchanger 44 (→ electric three-way valve 52) → second fixed throttle 53 ( → Three-way joint 54) → Outdoor heat exchanger 42 (→ first electric four-way valve 41) → first fixed throttle 15 → accumulator 14 → first compressor 11 The cycle in which the refrigerant circulates is configured.

  Therefore, in the heating operation mode of the present embodiment, the refrigerant discharged from the first compressor 11 is radiated by the use side heat exchanger 44 and switched to the refrigerant flow path for evaporating the refrigerant by the outdoor heat exchanger 42. ing.

  More specifically, the refrigerant flow path for causing the refrigerant radiated by the use side heat exchanger 44 to flow into the second fixed throttle 53 and evaporating the liquid phase refrigerant separated by the accumulator 14 by the outdoor heat exchanger 42. It has been switched to. Thereby, indoor ventilation air can be heated in the heating operation mode of this embodiment.

  As described above, in the ejector-type refrigeration cycle 40 of the present embodiment, in the cooling operation mode, the lowering of the flow rate of the drive flow of the ejector 13 is suppressed by the action of the second compressor 21 as in the ninth embodiment. The ejector refrigeration cycle can be stably operated and COP can be improved.

  More specifically, in the present embodiment, the refrigerant flow switching means 41, 51, 52, the ejector 13, and the second compression mechanism 21a similar to those in the ninth embodiment are provided. Even when the suction capacity of the ejector 13 is reduced in accordance with a decrease in the flow rate of the drive flow of the ejector 13 in at least one of the operation modes, the suction capacity of the ejector 13 is assisted by the second compression mechanism 21a. Can do.

  More specifically, it comprises an outflow-side gas-liquid separator 14 that separates the gas-liquid of the refrigerant that has flowed out of the diffuser section 13d, and a decompression means 52 that decompresses and expands the refrigerant in the heating operation mode, and an outflow-side gas-liquid separation The gas phase refrigerant outlet of the vessel 14 is connected to the inlet side of the first compression mechanism 11a, and the refrigerant flow switching means 41, 51, 52 are refrigerants that have radiated heat in the outdoor heat exchanger 42 in the cooling operation mode. Is switched to a refrigerant flow path that causes the liquid-phase refrigerant separated by the outflow-side gas-liquid separator 14 to evaporate in the use-side heat exchanger 44 and flow out to the suction side of the second compression mechanism 21a. In the heating operation mode, the refrigerant radiated by the use side heat exchanger 44 is caused to flow into the decompression means 52, and the liquid phase refrigerant separated by the outflow side gas-liquid separator 14 is evaporated by the outdoor heat exchanger 42. Outflow side gas-liquid Since the refrigerant flow path leading to the separator 14 is switched, the second compression mechanism 21a causes the ejector 13 even when the suction capacity of the ejector 13 is reduced in accordance with a decrease in the flow rate of the drive flow of the ejector 13 in the cooling operation mode. The suction ability can be assisted.

  As a result, the ejector refrigeration cycle can be stably operated in the cooling operation mode regardless of the fluctuation in the flow rate of the drive flow.

(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, 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.

  (2) In the above-described embodiments, examples in which electric compressors are employed as the first and second compressors 11 and 21 have been described. However, the formats 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.

  (3) In each of the above-described embodiments, the example in which the ejector refrigeration cycles 10 and 40 of the present invention are applied to a refrigerator and an air conditioner has been described. However, the application of the present invention is not limited to this. For example, the ejector refrigeration cycle 10 may be applied to other stationary refrigeration cycle apparatuses, vehicle air conditioners, and the like. Moreover, you may apply to the hot-water supply apparatus etc. which heat the water which is a heat exchange object fluid at the time of the heating operation mode of the ejector-type refrigerating cycle 20.

  (4) In each of the above-described embodiments, 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 configuration is configured such that the throttle passage area of the nozzle portion can be changed. An ejector may be employed. Similarly, a variable aperture mechanism may be adopted as the fixed aperture 15 and the second fixed aperture 53.

  (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 an ejector-type refrigeration cycle not provided with a high-pressure side decompression unit as in the first embodiment is configured as a supercritical refrigeration cycle, the high-pressure side refrigerant pressure increases, and the nozzle 13a inlet side pressure of the ejector 13 and the nozzle The pressure difference with the part 13a outlet side pressure 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.

  Furthermore, when configuring a supercritical refrigeration cycle, as the high pressure side decompression means, the high pressure side refrigerant pressure is determined based on the high pressure side refrigerant temperature on the outlet side of the radiator 12 so that the COP becomes substantially maximum. You may employ | adopt the pressure control valve adjusted to target high pressure.

As such a pressure control valve, specifically, there is a temperature sensing part provided on the outlet side of the radiator 12, and a pressure corresponding to the temperature of the high-pressure refrigerant on the outlet side of the radiator 12 inside the temperature sensing part. The valve opening degree can be adjusted by a mechanical mechanism based on the balance between the internal pressure of the temperature sensing portion and the refrigerant pressure on the outlet side of the radiator 12.
(6) In the above-described embodiment, the ejector refrigeration cycle in which the accumulator 14 is arranged on the downstream side of the diffuser portion 13d of the ejector 13 as described in Patent Document 1 has been described. However, the cycle configuration of the ejector refrigeration cycle is described here. It is not limited. By disposing the second compression mechanism 21a between the outlet side of the suction side evaporator and the refrigerant suction port of the ejector, the ejector refrigeration cycle can be stably operated even in other cycle configurations.

  Furthermore, although the above-mentioned embodiment demonstrated the ejector-type refrigeration cycle 10 and 40 provided only with the 1st, 2nd compression mechanisms 11a and 21a, you may provide an additional compression mechanism further. For example, with respect to the suction side evaporator 16 of the first embodiment, an additional evaporator is arranged in parallel, and an additional compression mechanism is provided so as to suck and compress only the refrigerant that has flowed out of this evaporator. May be.

  (7) In the first to seventh embodiments described above, the suction side evaporator 16 is configured as a use side heat exchanger, and the radiator 12 is configured as an outdoor heat exchanger that radiates heat to the atmosphere side. The side heat exchanger 16 may be configured as an outdoor heat exchanger that absorbs heat from a heat source such as the atmosphere, and the heat radiator 12 may be configured as a heat pump cycle configured as an indoor heat exchanger that heats a refrigerant to be heated such as air or water. .

  (8) In the above seventh to ninth embodiments, the temperature type expansion valve 17 is adopted as the high pressure side pressure reducing means, but the throttle opening (valve opening) can be adjusted by an external electric control signal. An electric expansion valve may be employed. Furthermore, a fixed throttle mechanism having the same configuration as that of the fixed throttle 15 may be used without using the variable throttle mechanism as the pressure reducing means.

  Further, as the high pressure side pressure reducing means and the low pressure side pressure reducing means (fixed throttle 15), an expander that expands and decompresses the refrigerant and converts the pressure energy of the refrigerant into mechanical energy and outputs it may be adopted. . 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 10 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.

  (9) A suction side gas-liquid separator 28 similar to that of the eighth embodiment may be added to the first to seventh embodiments. Thereby, only the gaseous-phase refrigerant | coolant isolate | separated by the suction side gas-liquid separator 28 can be supplied to the 2nd compression mechanism 21a, and the problem of the liquid compression of the 2nd compression mechanism 21a can be avoided reliably.

  (10) In the internal heat exchangers 30 to 32 of the above-described embodiments, 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 not mentioned. The refrigerant flow direction and the refrigerant flow direction in the low-pressure side refrigerant flow path may be parallel flows, and 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. It may be counterflow.

It is a whole block diagram of the ejector-type refrigerating cycle of 1st Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 1st Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 2nd Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 2nd Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 3rd Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 3rd Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 4th Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 4th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 5th Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 5th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 6th Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 6th Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 7th Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of the ejector-type refrigerating cycle of 7th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 8th Embodiment. It is a 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. 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

DESCRIPTION OF SYMBOLS 11, 12 1st, 2nd compressor 11a, 21a 1st, 2nd compression mechanism 11b, 21b 1st, 2nd electric motor 12 Radiator 12b Condensing part 12c Gas-liquid separation part 12d Supercooling part 13 Ejector 13a Nozzle part 13b Refrigerant suction port 13d Diffuser section 14 Accumulator 16 Suction side evaporator 17 Electric expansion valve 30, 31, 32 Internal heat exchanger 61 Outflow side evaporator

Claims (12)

A first compression mechanism (11a) for compressing and discharging the refrigerant;
A radiator (12) for radiating 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 part (13a) for decompressing and expanding the refrigerant flowing out of the radiator (12), and the jetted refrigerant and the refrigerant suction An ejector (13) that pressurizes the mixed refrigerant with the suction refrigerant sucked from the port (13b) at the diffuser section (13d);
A suction-side evaporator (16) that evaporates the refrigerant and flows it out to the refrigerant suction port (13b) side;
A second compression mechanism (21a) that sucks, compresses and discharges the suction-side evaporator (16) outlet-side refrigerant ;
First discharge capacity changing means (11b) for changing the refrigerant discharge capacity of the first compression mechanism (11a);
Second discharge capacity changing means (21b) for changing the refrigerant discharge capacity of the second compression mechanism (21a);
Control means for controlling the first discharge capacity changing means (11b) and the second discharge capacity changing means (21b),
The first discharge capacity changing means (11b) and the second discharge capacity changing means (21b) independently change the refrigerant discharge capacity of the first compression mechanism (11a) and the second compression mechanism (21a). Configured to be possible,
The control means includes the first discharge capacity changing means (11b) and the second pressure so that the pressure increase amount in the first compression mechanism (11a) is equal to the pressure increase amount in the second compression mechanism (21a). An ejector-type refrigeration cycle that controls the discharge capacity changing means (21b) . An outflow side gas-liquid separator (14) for separating the gas-liquid refrigerant flowing out of the diffuser section (13d),
The liquid refrigerant outlet of the outflow side gas-liquid separator (14) is connected to the inlet side of the suction side evaporator (16),
The ejector refrigeration cycle according to claim 1, wherein a gas-phase refrigerant outlet of the outflow side gas-liquid separator (14) is connected to the suction port side of the first compression mechanism (11a).   The ejector refrigeration cycle according to claim 2, further comprising an internal heat exchanger (30, 31, 32) for exchanging heat between the refrigerant flowing out of the radiator (12) and the low-pressure side refrigerant of the cycle.   The ejector-type refrigeration cycle according to claim 3, wherein the low-pressure side refrigerant of the cycle is a refrigerant sucked into the first compression mechanism (11a).   The ejector-type refrigeration cycle according to claim 3, wherein the low-pressure side refrigerant of the cycle is a refrigerant sucked into the second compression mechanism (21a).   The ejector refrigeration cycle according to claim 3, wherein the low-pressure side refrigerant of the cycle is a refrigerant inside the outflow side gas-liquid separator (14).   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 claim 1, wherein   The ejector according to claim 7, wherein the high-pressure side decompression means (17) is an expander that expands and decompresses the refrigerant and converts the pressure energy of the refrigerant into mechanical energy and outputs the mechanical energy. Refrigeration cycle.   The radiator (12) includes a condensing unit (12b) that condenses the refrigerant, a gas-liquid separating unit (12c) that separates the gas-liquid of the refrigerant that has flowed out of the condensing unit (12b), and the gas-liquid separating unit ( The ejector refrigeration cycle according to any one of claims 1 to 8, further comprising a supercooling section (12d) for supercooling the liquid-phase refrigerant that has flowed out of 12c). The said 1st compression mechanism (11a) and the said 2nd compression mechanism (21a) are accommodated in the same housing, and are comprised integrally, The any one of Claim 1 thru | or 9 characterized by the above-mentioned. The ejector-type refrigeration cycle described in 1. The ejector type refrigeration cycle according to any one of claims 1 to 10 , further comprising an outflow side evaporator (61) for evaporating the refrigerant flowing out of the diffuser section (13d). The ejector refrigeration cycle according to any one of claims 1 to 11 , wherein the first compression mechanism (11a) increases the pressure of the refrigerant until the pressure becomes equal to or higher than a critical pressure.

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