JP6642297B2 - Ejector refrigeration cycle - Google Patents

Description

  The present invention relates to an ejector refrigeration cycle including an ejector.

  BACKGROUND ART Conventionally, Patent Document 1 discloses an ejector refrigeration cycle that is a vapor compression refrigeration cycle device including an ejector as a refrigerant pressure reducing device.

  The ejector refrigeration cycle of Patent Document 1 is applied to an air conditioner. Further, the ejector-type refrigeration cycle of Patent Document 1 includes a cooling mode refrigerant circuit that cools blast air that is blown into the air-conditioned space, a heating mode refrigerant circuit that heats the blast air, and a humidified air that is cooled and dehumidified. The refrigerant circuit and the like in the weak dehumidification heating mode for heating are configured to be switchable.

  More specifically, in the ejector refrigeration cycle of Patent Document 1, in the weak dehumidification heating mode, the refrigerant flows through the indoor condenser, the outdoor heat exchanger, and the outdoor evaporator, the cooling heat exchanger, in the heating heat exchanger. To the refrigerant circuit connected in series. Then, the blown air is cooled and dehumidified by the indoor evaporator, and the dehumidified blown air is reheated by the indoor condenser.

  In this refrigerant circuit, the heating capacity of the blower air in the indoor condenser can be adjusted by adjusting the refrigerant pressure in the outdoor heat exchanger and adjusting the heat release amount of the refrigerant in the outdoor heat exchanger.

  Further, in the weak dehumidification heating mode, the refrigerant circuit is switched to a refrigerant circuit in which the refrigerant flowing out of the outdoor heat exchanger flows into the cooling-side nozzle portion of the cooling-side ejector. The refrigerant is supplied to the indoor evaporator by the suction effect of the injected refrigerant injected from the cooling-side nozzle portion. Further, the refrigerant compressed in the cooling-side diffuser section is sucked into the compressor to improve the coefficient of performance (COP) of the cycle.

JP 2014-206362 A

  However, according to the study of the present inventors, when the ejector-type refrigeration cycle of Patent Document 1 is actually operated, the blown air may not be able to be heated to a desired temperature in the weak dehumidification heating mode. . Then, when the present inventors investigated the cause, in the weak dehumidification heating mode of patent document 1, in order to increase the heating capacity of the blast air in the indoor condenser, the refrigerant pressure in the outdoor heat exchanger was reduced. Was found to be the cause.

  The reason is that if the refrigerant pressure in the outdoor heat exchanger is reduced, the pressure of the refrigerant flowing into the cooling-side nozzle portion also decreases, so that the cooling-side ejector cannot exert a sufficient suction action. . Then, the refrigerant cannot be supplied to the indoor evaporator, and the ejector refrigeration cycle cannot be operated properly. As a result, the blown air cannot be heated to a desired temperature.

  In other words, in the weak dehumidification heating mode of Patent Document 1, it is necessary to maintain the refrigerant pressure in the outdoor heat exchanger at a predetermined value or more in order to properly operate the ejector refrigeration cycle. For this reason, in the weak dehumidification heating mode of Patent Literature 1, the temperature adjustment range of the air blown into the air-conditioned space is limited.

  In view of the above, an object of the present invention is to expand the temperature adjustment range of blast air during dehumidifying and heating in an ejector refrigeration cycle applied to an air conditioner that performs dehumidifying and heating.

In order to achieve the above object, the invention according to claim 1 is an ejector type refrigeration cycle applied to an air conditioner,
A compressor (11) that compresses and discharges the refrigerant; a heat exchanger (12) that heats blast air that is blown into the air-conditioned space using the high-pressure refrigerant discharged from the compressor as a heat source; The refrigerant sucked from the refrigerant suction port (15c) by the suction action of the injected refrigerant injected from the nozzle portion (15a) for reducing the pressure of the refrigerant flowing out of the exchanger, and the refrigerant is sucked from the injected refrigerant and the suction refrigerant sucked from the refrigerant suction port. An ejector (15) having a pressure increasing section (15d) for increasing the pressure of the mixed refrigerant, a gas-liquid separator (19) for separating gas-liquid of the refrigerant flowing out of the ejector, and a decompression of the liquid-phase refrigerant flowing out of the gas-liquid separator. A first depressurizing device (14c), an outdoor heat exchanger (18) for exchanging heat between the refrigerant and the outside air, and a cooling heat exchange for evaporating the refrigerant and cooling the blast air before passing through the heating heat exchanger. Vessel (20) and cold It includes a second decompressor for decompressing a refrigerant flowing into use heat exchanger (14d), a refrigerant circuit switching device for switching the refrigerant circuit and (17 a - 17 e), and
The refrigerant circuit switching device is
In the heating mode in which the blast air is heated, the liquid-phase refrigerant separated by the gas-liquid separator flows into the outdoor heat exchanger through the first pressure reducing device, and the refrigerant flowing out of the outdoor heat exchanger flows into the refrigerant suction port. Switch to a refrigerant circuit that allows the gas-phase refrigerant separated by the gas-liquid separator to be sucked into the compressor,
In the series dehumidification heating mode in which the blast air cooled by the cooling heat exchanger is reheated by the heating heat exchanger, the refrigerant flowing out of the liquid-phase refrigerant outlet of the gas-liquid separator is passed through the first decompression device. A refrigerant circuit that flows into the outdoor heat exchanger, causes the refrigerant that has flowed out of the outdoor heat exchanger to flow into the cooling heat exchanger via the second decompression device, and sucks the refrigerant that has flowed out of the cooling heat exchanger into the compressor. This is an ejector type refrigeration cycle that switches to.

  According to this, in the heating mode, the refrigerant circuit switching device switches to the refrigerant circuit in which the gas-phase refrigerant separated by the gas-liquid separator (19) is drawn into the compressor (11). The refrigerant pressurized by the pressure increasing section (15d) can be sucked into the compressor (11). Therefore, the power consumption of the compressor (11) is reduced as compared with a normal refrigeration cycle device in which the refrigerant evaporation pressure in the outdoor heat exchanger (18) is equal to the suction refrigerant pressure of the compressor (11). The coefficient of performance (COP) can be improved.

  In the series dehumidification operation mode, the refrigerant circuit switching device converts the refrigerant flowing out of the liquid-phase refrigerant outlet of the gas-liquid separator (19) into the first pressure reducing device (14c) → the outdoor heat exchanger (18) → the second pressure reducing device. The system is switched to a refrigerant circuit that circulates in the order of the device (14d), the cooling heat exchanger (20), and the suction port of the compressor (11). Therefore, regardless of the refrigerant pressure in the outdoor heat exchanger (18), the refrigerant can be reliably supplied to the cooling heat exchanger (20) by the suction / discharge action of the compressor (11).

  Further, the refrigerant pressure in the outdoor heat exchanger (18) is adjusted to the refrigerant pressure in the cooling heat exchanger (20) by adjusting the throttle openings of the first pressure reducing device (14c) and the second pressure reducing device (14d). It can be reduced until it is equivalent. Thus, the amount of heat absorbed by the refrigerant in the outdoor heat exchanger (18) can be increased, and the amount of heat released by the refrigerant in the heating heat exchanger (12) can be increased. Therefore, the heating capacity of the blast air in the heating heat exchanger (12) can be expanded.

  At this time, since the refrigerant flowing out of the liquid-phase refrigerant outlet of the gas-liquid separator (19) can flow into the outdoor heat exchanger (18), the amount of heat absorbed by the refrigerant in the outdoor heat exchanger (18) is increased. be able to.

  As a result, according to the first aspect of the invention, the temperature adjustment range of the blown air during the dehumidifying and heating of the ejector refrigeration cycle applied to the air conditioner that performs the dehumidifying and heating can be expanded.

The invention according to claim 2 is an ejector-type refrigeration cycle applied to an air conditioner,
A compressor (11) that compresses and discharges the refrigerant; a heat exchanger (12) that heats blast air that is blown into the air-conditioned space using the high-pressure refrigerant discharged from the compressor as a heat source; Heating branch portion ( 13a ) for branching the flow of the refrigerant flowing out of the exchanger, and suction operation of the injected refrigerant injected from the nozzle portion (15a) for decompressing one of the refrigerants branched at the heating side branch portion. An ejector (15) having a booster (15d) for sucking refrigerant from the refrigerant suction port (15c) and increasing the pressure of a mixed refrigerant of the ejected refrigerant and the suction refrigerant sucked from the refrigerant suction port, and a refrigerant flowing out of the ejector A gas-liquid separator (19) for separating the gas-liquid, a first pressure reducing device (14c) for reducing the pressure of the liquid-phase refrigerant flowing out of the gas-liquid separator, and an outdoor heat exchanger ( 18) and the refrigerant A cooling heat exchanger (20) for emitting and cooling the blast air before passing through the heating heat exchanger, and a second pressure reducing device (14d) for reducing the pressure of the refrigerant flowing into the cooling heat exchanger (20). A third pressure reducing device (14a) for reducing the pressure of the other refrigerant branched at the heating-side branch portion, and a refrigerant circuit switching device (17b to 17f) for switching a refrigerant circuit,
The refrigerant circuit switching device is
In the heating mode in which the blast air is heated, the liquid-phase refrigerant separated by the gas-liquid separator flows into the outdoor heat exchanger through the first pressure reducing device, and the refrigerant flowing out of the outdoor heat exchanger flows into the refrigerant suction port. Switch to a refrigerant circuit that allows the gas-phase refrigerant separated by the gas-liquid separator to be sucked into the compressor,
In the series dehumidification heating mode in which the blast air cooled by the cooling heat exchanger is reheated by the heating heat exchanger, the refrigerant flowing out of the heating heat exchanger is passed through the third decompression device to the outdoor heat exchanger. And the refrigerant flowing out of the outdoor heat exchanger flows into the cooling heat exchanger via the second decompression device, and the refrigerant flowing out of the cooling heat exchanger flows into the gas-liquid separator, and the gas-liquid separation is performed. This is an ejector-type refrigeration cycle that switches to a refrigerant circuit that draws a gas-phase refrigerant separated by a compressor into a compressor.

  According to this, in the heating mode, the refrigerant circuit switching device switches to the refrigerant circuit in which the gas-phase refrigerant separated by the gas-liquid separator (19) is drawn into the compressor (11). The refrigerant pressurized by the pressure increasing section (15d) can be sucked into the compressor (11). Therefore, the power consumption of the compressor (11) can be reduced and the coefficient of performance (COP) of the cycle can be improved as compared with the ordinary refrigeration cycle apparatus, as in the first aspect of the invention.

  In the serial dehumidification operation mode, the refrigerant circuit switching device converts the refrigerant flowing out of the heating heat exchanger (12) into the third pressure reducing device (14a) → the outdoor heat exchanger (18) → the second pressure reducing device (14d). Switch to a refrigerant circuit that circulates in the order of cooling heat exchanger (20) → suction port of compressor (11). Therefore, regardless of the refrigerant pressure in the outdoor heat exchanger (18), the refrigerant can be reliably supplied to the cooling heat exchanger (20) by the suction / discharge action of the compressor (11).

  Further, the refrigerant pressure in the outdoor heat exchanger (18) is adjusted to the refrigerant pressure in the cooling heat exchanger (20) by adjusting the throttle openings of the third pressure reducing device (14a) and the second pressure reducing device (14d). It can be reduced until it is equivalent. Therefore, similarly to the first aspect of the present invention, it is possible to increase the heating capacity of the blowing air in the heating heat exchanger (12).

  As a result, according to the second aspect of the invention, it is possible to expand the temperature adjustment range of the blown air at the time of dehumidifying and heating of the ejector refrigeration cycle applied to the air conditioner for performing dehumidifying and heating.

  In addition, reference numerals in parentheses of each means described in this column and in the claims indicate a correspondence relationship with specific means described in the embodiment described later.

FIG. 2 is an overall configuration diagram illustrating a refrigerant circuit in a cooling mode and a weak series dehumidifying and heating mode of the ejector refrigeration cycle of the first embodiment. It is a whole block diagram which shows the refrigerant circuit at the time of the series dehumidification heating mode of the ejector type refrigerating cycle of 1st Embodiment. It is a whole block diagram which shows the refrigerant circuit at the time of the parallel dehumidification heating mode of the ejector type refrigerating cycle of 1st Embodiment. FIG. 2 is an overall configuration diagram illustrating a refrigerant circuit in a heating mode of the ejector refrigeration cycle of the first embodiment. It is a block diagram which shows the electric control part of the vehicle air conditioner of 1st Embodiment. FIG. 3 is a Mollier chart showing states of the refrigerant in a cooling mode of the ejector refrigeration cycle of the first embodiment. FIG. 2 is a Mollier chart showing a state of a refrigerant in a weak series dehumidification heating mode of the ejector refrigeration cycle of the first embodiment. FIG. 2 is a Mollier chart showing a state of a refrigerant in a series dehumidifying and heating mode of the ejector refrigeration cycle of the first embodiment. FIG. 3 is a Mollier diagram showing a state of a refrigerant in a parallel dehumidifying and heating mode of the ejector refrigeration cycle of the first embodiment. FIG. 2 is a Mollier diagram showing a state of a refrigerant in a heating mode of the ejector refrigeration cycle of the first embodiment. It is an explanatory view for explaining the temperature adjustable range of the blast air of the ejector refrigeration cycle of the first embodiment. It is a whole block diagram which shows the refrigerant circuit at the time of the cooling mode of the ejector type refrigerating cycle of 2nd Embodiment, and the series dehumidification heating mode. It is a whole block diagram which shows the refrigerant circuit at the time of the parallel dehumidification heating mode of the ejector type refrigerating cycle of 2nd Embodiment. It is a whole block diagram which shows the refrigerant circuit at the time of the heating mode of the ejector type refrigerating cycle of 2nd Embodiment.

(1st Embodiment)
A first embodiment of the present invention will be described with reference to FIGS. In the present embodiment, the ejector refrigeration cycle 10 according to the present invention is applied to a vehicle air conditioner 1 mounted on an electric vehicle that obtains a driving force for vehicle traveling from an electric motor for traveling. The ejector-type refrigeration cycle 10 has a function of heating or cooling the blast air blown into the vehicle interior, which is a space to be air-conditioned, in the vehicle air conditioner 1. Therefore, the heat exchange target fluid of the ejector refrigeration cycle 10 is blast air.

  Further, as shown in FIGS. 1 to 4, the ejector refrigeration cycle 10 includes a refrigerant circuit in a cooling mode (see FIG. 1), a refrigerant circuit in a weak series dehumidifying and heating mode (see FIG. 1), and a refrigerant in a series dehumidifying and heating mode. The circuit (see FIG. 2), the refrigerant circuit in the parallel dehumidification heating mode (see FIG. 3), and the refrigerant circuit in the heating mode (see FIG. 4) can be switched.

  The cooling mode is an operation mode in which the ventilation air is cooled to cool the passenger compartment. The weak series dehumidification and heating mode is an operation mode in which the air that has been cooled and dehumidified is reheated to perform dehumidification and heating in the vehicle interior. The series dehumidification heating mode is an operation mode in which the blowing air is reheated with a higher heating capacity than the weak series dehumidification heating mode to perform dehumidification heating in the vehicle compartment. The parallel dehumidification and heating mode is an operation mode in which the ventilation air is reheated with a higher heating capacity than the series dehumidification and heating mode to perform dehumidification and heating in the vehicle compartment. Further, the heating mode is an operation mode in which the ventilation air is heated to heat the vehicle interior. 1 to 4, the flow of the refrigerant in each operation mode is indicated by a solid line arrow.

  The ejector refrigeration cycle 10 employs an HFC-based refrigerant (specifically, R134a) as the refrigerant, and constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant. . This refrigerant contains refrigerating machine oil for lubricating the compressor 11, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.

  Among the components of the ejector-type refrigeration cycle 10, the compressor 11 is disposed in the hood of the vehicle and sucks, compresses, and discharges the refrigerant in the ejector-type refrigeration cycle 10. In the present embodiment, an electric compressor in which a fixed displacement compression mechanism having a fixed discharge capacity is rotationally driven by an electric motor is used as the compressor 11. The operation (rotation speed) of the compressor 11 is controlled by a control signal output from an air conditioning control device 40 described later.

  The refrigerant inlet side of the indoor condenser 12 is connected to a discharge port of the compressor 11. The indoor condenser 12 is disposed in a casing 31 that forms an air passage for the blown air in an indoor air conditioning unit 30 described later. The indoor condenser 12 is a heating heat exchanger that exchanges heat between the high-pressure refrigerant discharged from the compressor 11 and blast air that has passed through the indoor evaporator 20, which will be described later, and heats the blast air using the high-pressure refrigerant as a heat source. is there. The details of the indoor air conditioning unit 30 will be described later.

  One inlet / outlet side of the first three-way joint 13a is connected to the refrigerant outlet of the indoor condenser 12. Further, the ejector-type refrigeration cycle 10 includes second to fifth three-way joints 13b to 13e as described later. The basic configuration of the second to fifth three-way joints 13b to 13e is the same as that of the first three-way joint 13a.

  Among these three-way joints, for example, in the first three-way joint 13a in the cooling mode, one of the three inlets and outlets is used as a refrigerant inlet, and the other two are used as refrigerant outlets. Therefore, the first three-way joint 13a in the cooling mode functions as a branching portion that branches the flow of the refrigerant flowing from the refrigerant inflow port.

  Further, for example, in the fifth three-way joint 13e in the parallel dehumidifying and heating mode, two of the three inflow / outflow ports are used as refrigerant inflow ports, and the remaining one is used as a refrigerant outflow port. Therefore, the fourth three-way joint 13d in the parallel dehumidifying and heating mode functions as a joining portion for joining the refrigerant flowing from the two refrigerant inlets.

  One refrigerant outlet of the first three-way joint 13a is connected to a refrigerant inlet side of the second three-way joint 13b via a first flow control valve 14a. The other refrigerant outlet of the first three-way joint 13a is connected to an inlet side of a nozzle portion 15a of an ejector 15 described later via a second flow control valve 14b.

  Each of the first and second flow control valves 14a and 14b has a valve body that changes the opening degree of the refrigerant passage, and an electric actuator (specifically, a stepping motor) that changes the opening degree of the valve body. This is an electric variable aperture mechanism composed of:

  The first flow control valve 14a functions as an expansion valve that adjusts the flow rate of the refrigerant flowing into the outdoor heat exchanger 18, which will be described later, and decompresses the refrigerant, at least in the weak series dehumidifying and heating mode. The second flow control valve 14b functions to adjust the flow rate of the refrigerant flowing into the nozzle portion 15a of the ejector 15 and to function as an expansion valve for reducing the pressure of the refrigerant at least in the parallel dehumidifying heating mode and the heating mode.

  Further, the ejector type refrigeration cycle 10 includes third and fourth flow control valves 14c and 14d as described later. The basic configuration of the third and fourth flow control valves 14c and 14d is the same as that of the first and second flow control valves 14a and 14b.

  These first to fourth flow control valves 14a to 14d have a fully open function that functions as a mere refrigerant passage without exerting a flow control function and a refrigerant pressure reducing function by fully opening the valve opening degree, and a valve opening degree. Has a fully closed function of closing the refrigerant flow path by fully closing.

By the full opening function and fully closed function, first to fourth flow regulating valve 14a~14d can switch the refrigerant circuit of the operating modes above mentioned. Therefore, the first to fourth flow control valves 14a to 14d also have a function as a refrigerant circuit switching device for switching the refrigerant circuit. The operation of the first to fourth flow control valves 14 a to 14 d is controlled by a control signal (control pulse) output from the air conditioning control device 40.

  One inflow / outlet side of the third three-way joint 13c is connected to one refrigerant outlet of the second three-way joint 13b. The other refrigerant outlet of the second three-way joint 13b is connected to one refrigerant inlet side of the fourth three-way joint 13d via a refrigerant passage 16a for dehumidifying and heating.

  A first on-off valve 17a is provided in a refrigerant passage connecting one refrigerant outlet of the second three-way joint 13b and one inlet / outlet side of the third three-way joint 13c. A second on-off valve 17b is disposed in the dehumidifying and heating refrigerant passage 16a.

  Each of the first and second on-off valves 17a and 17b is an electromagnetic valve that opens and closes a refrigerant passage. More specifically, the second on-off valve 17b is an on-off valve for dehumidifying and heating that opens and closes the refrigerant passage 16a for dehumidifying and heating. Further, the ejector refrigeration cycle 10 includes third to fifth on-off valves 17c to 17e, as described later. The basic configuration of the third to fifth on-off valves 17c to 17e is the same as that of the first and second on-off valves 17a and 17b.

  Further, the first to fifth on-off valves 17a to 17e can switch the refrigerant circuit in each of the above-described operation modes by opening and closing the refrigerant passage. Therefore, the first to fifth on-off valves 17a to 17e function as a refrigerant circuit switching device together with the first to fourth flow control valves 14a to 14d. The operation of the first to fifth on-off valves 17 a to 17 e is controlled by a control voltage output from the air conditioning control device 40.

  One refrigerant inflow / outlet side of the outdoor heat exchanger 18 is connected to another inflow / outflow port of the third three-way joint 13c. The refrigerant suction port 15c side of the ejector 15 is connected to another inflow / outflow port of the third three-way joint 13c. A third on-off valve 17c for opening and closing the refrigerant passage is arranged in a refrigerant passage connecting another inflow / outlet of the third three-way joint 13c and the refrigerant suction port 15c of the ejector 15.

  The ejector 15 functions as a decompression device that decompresses the refrigerant flowing out of the indoor condenser 12 at least in the parallel dehumidifying heating mode and the heating mode. Further, the ejector 15 functions as a refrigerant transport device that sucks and transports the refrigerant flowing out of the outdoor heat exchanger 18 by a suction action of the injected refrigerant that is injected at a high speed.

  More specifically, the ejector 15 has a nozzle part 15a and a body part 15b. The nozzle portion 15a is formed of a substantially cylindrical member made of metal (in this embodiment, stainless steel) having a shape that gradually tapers in the flow direction of the refrigerant. Then, the refrigerant is isentropically decompressed in the refrigerant passage formed therein.

  A throat portion (minimum passage area portion) having the smallest passage cross-sectional area is formed in the refrigerant passage formed inside the nozzle portion 15a. As a result, a divergent portion is formed to increase the refrigerant passage area. That is, the nozzle portion 15a is configured as a Laval nozzle.

  Further, in the present embodiment, the nozzle portion 15a that is set so that the flow rate of the injected refrigerant injected from the refrigerant injection port is equal to or higher than the sonic speed during normal operation of the ejector refrigeration cycle 10 is employed. Of course, the nozzle portion 15a may be formed by a tapered nozzle.

  The body portion 15b is formed of a cylindrical member made of metal (in this embodiment, aluminum alloy), functions as a fixing member for supporting and fixing the nozzle portion 15a inside, and forms an outer shell of the ejector 15. Is what you do. More specifically, the nozzle portion 15a is press-fitted and fixed so as to be housed inside one end in the longitudinal direction of the body portion 15b. Therefore, the refrigerant does not leak from the fixed portion (press-fit portion) between the nozzle portion 15a and the body portion 15b.

  Further, a portion of the outer peripheral surface of the body portion 15b corresponding to the outer peripheral side of the nozzle portion 15a has a refrigerant suction port 15c provided so as to penetrate the inside and outside thereof and communicate with the refrigerant injection port of the nozzle portion 15a. Is formed. The refrigerant suction port 15c is a through hole that sucks the refrigerant flowing out of the outdoor heat exchanger 18 into the ejector 15 by a suction action of the refrigerant injected from the nozzle part 15a.

  Further, inside the body portion 15b, a suction passage for guiding the suction refrigerant sucked from the refrigerant suction port 15c to the refrigerant ejection port side of the nozzle portion 15a, and a suction refrigerant flowing into the ejector 15 via the suction passage, A diffuser section 15d, which is a pressure increasing section that mixes with the injection refrigerant to increase the pressure, is formed.

The diffuser portion 15d is disposed so as to be continuous to the outlet of the suction passage path, the refrigerant passage area is formed so as to gradually expand. Thereby, the function of increasing the pressure of the mixed refrigerant of the injected refrigerant and the suction refrigerant by reducing the flow velocity while mixing the injected refrigerant and the suction refrigerant, that is, the function of converting the velocity energy of the mixed refrigerant into the pressure energy Fulfill.

  The inlet side of the accumulator 19 is connected to the refrigerant outlet of the diffuser section 15d. The accumulator 19 is a gas-liquid separator that separates gas-liquid refrigerant flowing out of the diffuser 15 d of the ejector 15. The accumulator 19 is provided with a gas-phase refrigerant outlet for letting out the separated gas-phase refrigerant, and two liquid-phase refrigerant outlets for letting out the separated liquid-phase refrigerant.

  One refrigerant inflow port of the fifth three-way joint 13e is connected to the gaseous phase refrigerant outflow port of the accumulator 19. A fourth on-off valve 17d is disposed in a refrigerant passage connecting the gas-phase refrigerant outlet of the accumulator 19 and one refrigerant inlet of the fifth three-way joint 13e.

  The other refrigerant inflow side of the fourth three-way joint 13d to which the above-described dehumidification and heating refrigerant passage 16a is connected is connected to one liquid phase refrigerant outflow port of the accumulator 19. A fifth on-off valve 17e is disposed in a refrigerant passage connecting one liquid-phase refrigerant outlet of the accumulator 19 and the other refrigerant inlet of the fourth three-way joint 13d.

  The other refrigerant inflow / outlet side of the outdoor heat exchanger 18 is connected to the other liquid phase refrigerant outflow port of the accumulator 19. A third flow control valve 14c is disposed in a refrigerant passage connecting the other liquid phase refrigerant outlet of the accumulator 19 and the other refrigerant inlet / outlet of the outdoor heat exchanger 18. The third flow control valve 14c is a first pressure reducing device that reduces the pressure of the liquid refrigerant flowing out of the accumulator 19 at least in the heating mode.

  The outdoor heat exchanger 18 is a heat exchanger that is disposed in the hood of the vehicle and exchanges heat between the refrigerant flowing inside the hood and the outside air blown from a blower fan (not shown). The outdoor heat exchanger 18 functions as a radiator that radiates high-pressure refrigerant in the cooling mode and the weak series dehumidifying and heating mode. Furthermore, in the series dehumidification heating mode, the parallel dehumidification heating mode, and the heating mode, it functions as an evaporator for evaporating the refrigerant.

  Further, in the present embodiment, the outdoor heat exchanger 18 in which the cross-sectional area of the refrigerant passage formed inside changes in the refrigerant flow direction is adopted. More specifically, the outdoor heat exchanger 18 of the present embodiment is configured by a so-called tank-and-tube heat exchanger. The passage cross-sectional area of the refrigerant passage formed inside is changed by adjusting the path configuration through which the refrigerant flows.

  Here, the path in the tank-and-tube type heat exchanger is a group of tubes that allows the refrigerant in the same distribution space formed in the tank to flow in the same direction toward the same collective space formed in the tank. Can be defined as a refrigerant passage formed by Therefore, by changing the number of tubes constituting the path, the passage cross-sectional area of the path (refrigerant passage) (total passage cross-sectional area of the tubes) can be changed.

In the outdoor heat exchanger 18 of the present embodiment, a passage configuration in which the passage cross-sectional area of the refrigerant passage formed therein gradually increases as going from the other refrigerant inflow / outlet side to the one refrigerant inflow / outlet side is adopted. Has become. Incidentally, the other refrigerant inflow outlet that put the present embodiment becomes an inflow outlet the other liquid refrigerant flow outlet side of the accumulator 19 is connected, one of the refrigerant inlet outlet, another inflow outlet of the third three-way joint 13c Side is the inflow / outlet to be connected.

  The refrigerant outlet of the indoor evaporator 20 is connected to the refrigerant outlet of the fourth three-way joint 13d. A fourth flow control valve 14d is disposed in a refrigerant passage connecting the refrigerant outlet of the fourth three-way joint 13d and the refrigerant inlet of the indoor evaporator 20. The fourth flow control valve 14d is a second decompression device that decompresses the refrigerant flowing into the indoor evaporator 20 at least in the cooling mode, the weak series dehumidification / heating mode, the series dehumidification / heating mode, and the parallel dehumidification / heating mode.

  For this reason, the refrigerant passage 16a for dehumidifying and heating of the present embodiment connects the refrigerant inflow / outflow port on the third three-way joint 13c side and the inlet port of the fourth flow control valve 14d as the second pressure reducing device.

  The indoor evaporator 20 is arranged in the casing 31 of the indoor air conditioning unit 30 and on the upstream side of the indoor condenser 12 in the air flow. The indoor evaporator 20 is a cooling heat exchanger that cools the blown air by exchanging heat with the blown air and evaporating the low-pressure refrigerant depressurized by the fourth flow control valve 14d and exerting a heat absorbing action.

  The refrigerant outlet of the indoor evaporator 20 is connected to the other refrigerant inlet of the fifth three-way joint 13e described above. The refrigerant outlet of the fifth three-way joint 13e is connected to the suction port of the compressor 11.

  Next, the indoor air conditioning unit 30 will be described. The indoor air-conditioning unit 30 is for blowing out blast air, the temperature of which has been adjusted by the ejector refrigeration cycle 10, into the vehicle interior, and is disposed inside (vehicle interior) the instrument panel (instrument panel) at the forefront of the vehicle interior. I have. The indoor air-conditioning unit 30 is configured by housing a blower 32, an indoor evaporator 20, an indoor condenser 12, an air mixing door 34, and the like in a casing 31 forming an outer shell thereof.

  The casing 31 forms an air passage for blowing air blown into the vehicle interior, and is formed of a resin (for example, polypropylene) having a certain degree of elasticity and excellent strength. An inside / outside air switching device 33 serving as inside / outside air switching means for switching and introducing inside air (vehicle interior air) and outside air (vehicle outside air) into the casing 31 is disposed on the most upstream side of the flow of the blown air in the casing 31. ing.

  The inside / outside air switching device 33 continuously adjusts the opening area of the inside air introduction port for introducing the inside air into the casing 31 and the outside air introduction port for introducing the outside air by the inside / outside air switching door, so that the inside air volume and the outside air volume are adjusted. Is continuously changed. The inside / outside air switching door is driven by an electric actuator for the inside / outside air switching door, and the operation of the electric actuator is controlled by a control signal output from the air conditioning control device 40.

  A blower (blower) 32 is disposed downstream of the inside / outside air switching device 33 as a blowing unit that blows air sucked through the inside / outside air switching device 33 toward the vehicle interior. The blower 32 is an electric blower that drives a centrifugal multi-blade fan (sirocco fan) with an electric motor, and the number of rotations (blowing amount) is controlled by a control voltage output from the air conditioning controller 40.

  The indoor evaporator 20 and the indoor condenser 12 are arranged in this order on the downstream side of the blower air flow of the blower 32. That is, the indoor evaporator 20 is disposed on the upstream side of the flow of the blown air from the indoor condenser 12. Further, on the downstream side of the air flow of the indoor evaporator 20 and on the upstream side of the blown air flow of the indoor condenser 12, the air volume of the blown air after passing through the indoor evaporator 20, which passes through the indoor condenser 12. An air mix door 34 for adjusting the ratio is provided.

  Further, on the downstream side of the air flow of the indoor condenser 12, the blown air heated by exchanging heat with the refrigerant in the indoor condenser 12 and the blown air that is not heated by bypassing the indoor condenser 12 are mixed. A mixing space 35 is provided. Further, an opening hole for blowing the blast air (air-conditioned air) mixed in the mixing space 35 into the vehicle interior, which is a space to be air-conditioned, is provided at the most downstream portion of the air flow of the air in the casing 31.

  Specifically, a face opening, a foot opening, and a defroster opening (all not shown) are provided as the opening. The face opening hole is an opening hole for blowing out conditioned air toward the upper body of the occupant in the passenger compartment. The foot opening hole is an opening hole for blowing out conditioned air toward the feet of the occupant. The defroster opening hole is an opening hole for blowing out conditioned air toward the inner surface of the vehicle front window glass.

  The face opening, the foot opening, and the defroster opening are respectively formed by a face opening, a foot opening, and a defroster opening provided in the vehicle cabin through ducts forming air passages. )It is connected to the.

  Therefore, the temperature of the conditioned air mixed in the mixing space is adjusted by the air mix door 34 adjusting the air flow ratio of the air flow passing through the indoor condenser 12 and the air flow bypassing the indoor condenser 12. . As a result, the temperature of the blown air (conditioned air) blown out from each outlet into the vehicle compartment is adjusted.

  That is, the air mix door 34 functions as a temperature adjustment unit that adjusts the temperature of the conditioned air blown into the vehicle interior. The air mix door 34 is driven by an electric actuator for driving the air mix door, and the operation of the electric actuator is controlled by a control signal output from the air conditioning controller 40.

  In addition, a face door for adjusting the opening area of the face opening hole, a foot door for adjusting the opening area of the foot opening hole, and a defroster opening are provided on the upstream side of the blown air flow of the face opening hole, the foot opening hole, and the defroster opening hole, respectively. A defroster door (both not shown) for adjusting the opening area of the hole is arranged.

  These face doors, foot doors, and defroster doors constitute an opening hole mode switching device that switches the opening hole mode, and are linked to an electric actuator for driving the outlet mode door via a link mechanism and interlocked. And rotated. The operation of this electric actuator is also controlled by a control signal output from the air conditioning control device 40.

  Specific examples of the outlet mode switched by the outlet mode switching device include a face mode, a bi-level mode, and a foot mode.

  The face mode is an outlet mode in which the face outlet is fully opened and air is blown from the face outlet toward the upper body of the passenger in the vehicle compartment. The bi-level mode is an air outlet mode in which both the face air outlet and the foot air outlet are opened to blow air toward the upper body and feet of the occupant in the vehicle. The foot mode is an outlet mode in which the foot outlet is fully opened and the defroster outlet is opened by a small opening, and air is mainly blown out from the foot outlet.

  Further, the occupant can manually operate the air outlet mode changeover switch provided on the operation panel 50 to fully open the defroster air outlet, thereby setting a defroster mode in which air is blown from the defroster air outlet to the inner surface of the vehicle windshield.

  Next, the electric control unit of the present embodiment will be described. The air-conditioning control device 40 is composed of a well-known microcomputer including a CPU, a ROM, a RAM, and the like, and its peripheral circuits, performs various calculations and processes based on a control program stored in the ROM, and is connected to an output side. The operation of the various control target devices 11, 14a to 14d, 17a to 17e, and 32 is controlled.

  On the input side of the air conditioning control device 40, as shown in the block diagram of FIG. 5, an inside air temperature sensor 41, an outside air temperature sensor 42, a solar radiation sensor 43, an outdoor heat exchanger temperature sensor 44, a discharge temperature sensor 45, An evaporator temperature sensor 46, an air conditioning air temperature sensor 47, and the like are connected. Then, the detection signals of these sensor groups are input to the air conditioning control device 40.

  The internal air temperature sensor 41 is an internal air temperature detecting unit that detects the vehicle interior temperature (internal air temperature) Tr. The outside air temperature sensor 42 is an outside air temperature detection unit that detects a vehicle outside temperature (outside air temperature) Tam. The solar radiation sensor 43 is a solar radiation amount detector that detects the amount of solar radiation As emitted to the vehicle interior. The outdoor heat exchanger temperature sensor 44 is an outdoor heat exchanger temperature detection unit that detects the temperature (outdoor heat exchanger temperature) Tout of the refrigerant in the outdoor heat exchanger. The discharge temperature sensor 45 is a discharge temperature detection unit that detects a refrigerant discharge temperature Td of the compressor 11. The indoor evaporator temperature sensor 46 is an evaporator temperature detecting unit that detects a refrigerant evaporation temperature (indoor evaporator temperature) Tefin in the indoor evaporator 20. The air-conditioning air temperature sensor 47 is an air-conditioning air temperature detecting unit that detects the temperature of the air blown from the mixing space into the vehicle compartment TAV.

  Further, as shown in FIG. 5, an operation panel 50 disposed near the instrument panel in the front of the vehicle compartment is connected to the input side of the air conditioning control device 40, and various operation switches provided on the operation panel 50 are provided. Is input. The various operation switches provided on the operation panel 50 include an auto switch, a cooling switch (A / C switch), an air volume setting switch, a temperature setting switch, a blowing mode switching switch, and the like.

  The auto switch is an input unit for setting or canceling the automatic control operation of the vehicle air conditioner 1. The cooling switch (A / C switch) is an input unit for requesting to perform cooling in the passenger compartment. The air volume setting switch is an input unit for manually setting the air volume of the blower 32. The temperature setting switch is an input unit for manually setting the target temperature Tset in the vehicle compartment. The blowing mode changeover switch is an input unit for manually setting the blowing mode.

  The air-conditioning control device 40 according to the present embodiment is configured such that a control unit that controls various control target devices connected to an output side thereof is integrally formed, but a configuration that controls the operation of each control target device. (Hardware and software) constitute a control unit that controls the operation of each control target device.

  For example, in the air-conditioning control device 40, a configuration that controls the refrigerant discharge capacity of the compressor 11 (the number of revolutions of the compressor 11) forms a discharge capacity control unit. The configuration for controlling the operation of the refrigerant circuit switching devices such as the first to fifth on-off valves 17a to 17e constitutes a refrigerant circuit control unit.

  Next, the operation of the present embodiment in the above configuration will be described. As described above, in the ejector type refrigeration cycle 10 of the present embodiment, the operation in the cooling mode, the weak series dehumidification heating mode, the series dehumidification heating mode, the parallel dehumidification heating mode, and the heating mode can be switched.

  Switching of these operation modes is performed by executing an air conditioning control program stored in advance in a storage circuit of the air conditioning control device 40. The air conditioning control program is executed when the auto switch of the operation panel 50 is turned on (ON).

More specifically, in the main routine of the air conditioning control program, detection signals of the above-described air conditioning control sensor group and operation signals from various air conditioning operation switches are read. Then, based on the values of the read detection signal and operation signal, a target outlet temperature TAO, which is a target temperature of the outlet air to be blown into the vehicle interior, is calculated based on the following equation F1.
TAO = Kset × Tset−Kr × Tr−Kam × Tam−Ks × As + C (F1)
Here, Tset is the vehicle interior set temperature set by the temperature setting switch, Tr is the vehicle interior temperature (internal temperature) detected by the internal air sensor, Tam is the external air temperature detected by the external air sensor, and As is detected by the solar radiation sensor. Is the amount of solar radiation. Kset, Kr, Kam, and Ks are control gains, and C is a correction constant.

  Further, when the cooling switch of the operation panel 50 is turned on and the target blowing temperature TAO is lower than the predetermined cooling reference temperature α, the operation in the cooling mode is executed.

  When the cooling switch is turned on, the target outlet temperature TAO is equal to or higher than the cooling reference temperature α, the outside air temperature Tam is higher than the predetermined dehumidifying heating reference temperature β, and the outdoor heat exchange is further performed. When the outdoor heat exchanger temperature Tout detected by the unit temperature sensor 44 is higher than the outside air temperature Tam, the operation in the weak series dehumidifying heating mode is performed.

  In a state where the cooling switch is turned on, the target outlet temperature TAO is equal to or higher than the cooling reference temperature α, the outside air temperature Tam is higher than the dehumidifying heating reference temperature β, and the outdoor heat exchanger temperature Tout Is lower than the outside temperature Tam, the operation in the in-line dehumidifying and heating mode is executed.

  If the target air temperature TAO is equal to or higher than the cooling reference temperature α and the outside air temperature Tam is equal to or lower than the dehumidifying heating reference temperature β while the cooling switch is turned on, the parallel dehumidifying and heating mode is set. Perform the operation at. Then, when the cooling switch is not turned on, the operation in the heating mode is executed.

  Thereby, in the vehicle air conditioner 1 of the present embodiment, the operation in the cooling mode is executed mainly when the outside air temperature is relatively high as in summer. In addition, mainly in early spring or early winter, the operation in the weak series dehumidification heating mode, the series dehumidification heating mode, and the parallel dehumidification heating mode is performed. The operation in the heating mode is mainly performed when the outside air temperature is relatively low, such as in winter. The operation in each operation mode will be described below.

(A) Cooling Mode In the cooling mode, the air-conditioning control device 40 fully opens the first flow control valve 14a, fully closes the second flow control valve 14b, fully opens the third flow control valve 14c, and performs fourth flow control. The valve 14d is set to a throttle state for exerting the refrigerant pressure reducing action. Further, the air conditioning controller 40 opens the first on-off valve 17a, closes the second on-off valve 17b, closes the third on-off valve 17c, closes the fourth on-off valve 17d, and opens the fifth on-off valve 17e.

  Thereby, in the cooling mode, as shown by the solid arrow in FIG. 1, the compressor 11 → the indoor condenser 12 (→ the first flow control valve 14a) → the outdoor heat exchanger 18 (→ the third flow control valve 14c) → A refrigeration cycle in which the refrigerant circulates in the order of the accumulator 19 → the fourth flow control valve 14d → the indoor evaporator 20 → the compressor 11 is configured.

  With the configuration of the refrigerant circuit, the air-conditioning control device 40 determines the operation states of various control target devices (control signals to be output to various control target devices) based on the target blowout temperature TAO, detection signals of the sensor group, and the like.

  For example, the refrigerant discharge capacity of the compressor 11, that is, the control signal output to the electric motor of the compressor 11, is determined as follows. First, based on the target outlet temperature TAO, a target evaporator outlet temperature TEO of the indoor evaporator 20 is determined with reference to a control map stored in the air conditioning controller 40 in advance. The target evaporator outlet temperature TEO is determined to be equal to or higher than a reference frost prevention temperature (for example, 1 ° C.) determined to be able to suppress frost formation on the indoor evaporator 20.

  Then, based on the deviation between the target evaporator outlet temperature TEO and the indoor evaporator temperature Tefin detected by the indoor evaporator temperature sensor 46, the indoor evaporator temperature Tefin is changed to the target evaporator outlet temperature TEO using a feedback control method. The control signal output to the electric motor of the compressor 11 is determined so as to approach.

  The degree of opening of the fourth flow control valve 14d, that is, the control signal (control pulse) output to the fourth flow control valve 14d, is determined based on a predetermined degree of superheat of the refrigerant sucked into the compressor 11. It is determined to approach the degree of superheat.

  In addition, regarding the control signal output to the electric actuator that drives the air mix door 34, the air mix door 34 closes the air passage on the indoor condenser 12 side, and the total flow rate of the blown air after passing through the indoor evaporator 20 is reduced. It is determined to flow around the indoor condenser 12.

  Then, the control signal and the like determined as described above are output to various control target devices. After that, until the operation stop of the vehicle air conditioner 1 is requested, the above-described detection signal and operation signal are read at every predetermined control cycle → calculation of the target blowout temperature TAO → decision of operation states of various control target devices → control A control routine such as outputting the voltage and the control signal is repeated. The repetition of such a control routine is similarly performed in other operation modes.

  Accordingly, in the ejector refrigeration cycle 10 in the cooling mode, the state of the refrigerant changes as shown in the Mollier diagram of FIG.

  Specifically, the high-pressure refrigerant (point a6 in FIG. 6) discharged from the compressor 11 flows into the indoor condenser 12. At this time, since the air mix door 34 closes the air passage on the indoor condenser 12 side, the refrigerant flowing into the indoor condenser 12 flows out of the indoor condenser 12 with almost no heat exchange with the blown air.

  The refrigerant flowing out of the indoor condenser 12 passes through the first three-way joint 13a, the fully opened first flow control valve 14a, the second three-way joint 13b, and the third three-way joint 13c. The refrigerant flows into one refrigerant inlet / outlet. The refrigerant flowing into the outdoor heat exchanger 18 radiates heat to the outside air blown from the blower fan in the outdoor heat exchanger 18 and condenses (point a6 → point e6 in FIG. 6).

  The refrigerant flowing out from the other refrigerant inlet / outlet of the outdoor heat exchanger 18 flows into the accumulator 19 via the fully opened third flow control valve 14c, and is separated into gas and liquid. The liquid-phase refrigerant separated by the accumulator 19 flows into the throttled fourth flow control valve 14d via the fourth three-way joint 13d and is reduced in pressure (point e6 → point g6 in FIG. 6). .

  The refrigerant decompressed by the fourth flow control valve 14d flows into the indoor evaporator 20, and exchanges heat with the blast air blown from the blower 32 to evaporate (point g6 → point h6 in FIG. 6). Thereby, the blown air is cooled. The refrigerant flowing out of the indoor evaporator 20 is sucked into the compressor 11 via the fifth three-way joint 13e and compressed again (point h6 → point a6 in FIG. 6).

  Therefore, in the cooling mode, the air in the vehicle compartment can be cooled by blowing the blast air cooled by the indoor evaporator 20 into the vehicle compartment without being reheated by the indoor condenser 12.

(B) Weak series dehumidification and heating mode In the weak series dehumidification and heating mode, the air conditioning controller 40 closes the first flow control valve 14a, fully closes the second flow control valve 14b, and closes the third flow control valve 14c. The valve is fully opened, and the fourth flow control valve 14d is set in the throttled state. Further, the air conditioning controller 40 opens the first on-off valve 17a, closes the second on-off valve 17b, closes the third on-off valve 17c, closes the fourth on-off valve 17d, and opens the fifth on-off valve 17e.

  Thereby, in the weak series dehumidification heating mode, as shown by the solid arrow in FIG. 1, the compressor 11 → the indoor condenser 12 → the first flow control valve 14a → the outdoor heat exchanger 18 (→ the third flow control valve 14c). → The accumulator 19 → the fourth flow control valve 14d → the indoor evaporator 20 → the refrigeration cycle in which the refrigerant circulates in the same order as in the cooling mode of the compressor 11 is configured. For this reason, in the weak series dehumidification heating mode, the outdoor heat exchanger 18 and the indoor evaporator 20 are connected in series to the refrigerant flow.

  With the configuration of the refrigerant circuit, the air-conditioning control device 40 determines the operation states of various control target devices (control signals to be output to various control target devices) based on the target blowout temperature TAO, the detection signals of the sensor group, and the like.

  For example, the throttle opening of the first flow control valve 14a, that is, the control signal (control pulse) output to the first flow control valve 14a is stored in the air conditioning control device 40 in advance based on the target outlet temperature TAO. It is determined with reference to the control map. Specifically, the throttle opening is determined to decrease as the target outlet temperature TAO increases. In other words, the throttle opening is determined to decrease with an increase in the heating capacity required for the cycle.

  Further, the throttle opening of the fourth flow control valve 14d is determined so that the degree of superheat of the suction refrigerant approaches the predetermined reference degree of superheat, as in the cooling mode. Therefore, the throttle opening of the fourth flow control valve 14d increases as the throttle opening of the first flow control valve 14a decreases. In other words, it is determined that the throttle opening increases as the heating capacity required for the cycle increases.

  The opening degree of the air mix door 34, that is, the control signal output to the electric actuator that drives the air mix door 34, is such that the blast air temperature TAV detected by the conditioned air temperature sensor 47 approaches the target outlet temperature TAO. Is determined. The operating states of the other control target devices are determined in the same manner as in the cooling mode.

  Therefore, in the ejector refrigeration cycle 10 in the weak series dehumidification heating mode, the state of the refrigerant changes as shown in the Mollier diagram of FIG. In the Mollier diagram of FIG. 7, the state of the refrigerant at the same position in the cycle configuration as the Mollier diagram of FIG. 6 described in the cooling mode is indicated by the same reference numeral (alphabet) as in FIG. Has changed. This is the same in other Mollier diagrams described below.

  Specifically, in the weak series dehumidifying and heating mode, the air mix door 34 opens the blast air passage on the side of the indoor condenser 12, so that the high-pressure refrigerant (point a7 in FIG. 7) discharged from the compressor 11 is condensed in the room. It flows into the vessel 12 and exchanges heat with a part of the blown air cooled and dehumidified by the indoor evaporator 20 to radiate heat (point a7 → point b7 in FIG. 7). Thereby, a part of the blowing air is heated.

  The refrigerant flowing out of the indoor condenser 12 flows into the first flow control valve 14a via the first three-way joint 13a and is decompressed (point b7 → point c7 in FIG. 7). The refrigerant decompressed by the first flow control valve 14a flows into one refrigerant inlet / outlet of the outdoor heat exchanger 18 via the second three-way joint 13b and the third three-way joint 13c.

  In the weak series dehumidifying and heating mode, the outdoor heat exchanger temperature Tout is higher than the outdoor temperature Tam, so the refrigerant flowing into the outdoor heat exchanger 18 is supplied to the outside air blown from the blower fan by the outdoor heat exchanger 18. The heat is dissipated (point c7 → point e7 in FIG. 7). The refrigerant flowing out of the other refrigerant inflow / outflow port of the outdoor heat exchanger 18 flows into the accumulator 19 via the fully opened third flow control valve 14c and is separated into gas and liquid. Subsequent operations are the same as in the cooling mode.

  Therefore, in the weak series dehumidifying and heating mode, the air that has been cooled and dehumidified by the indoor evaporator 20 is reheated by the indoor condenser 12 and blown out into the vehicle interior, thereby performing dehumidification and heating in the vehicle interior. it can.

  In the weak series dehumidifying and heating mode, the temperature of the refrigerant flowing into the outdoor heat exchanger 18 is lower than in the cooling mode by setting the first flow control valve 14a in the throttled state. Therefore, the temperature difference between the temperature of the refrigerant in the outdoor heat exchanger 18 and the outside air temperature can be reduced more than in the cooling mode, and the heat release amount of the refrigerant in the outdoor heat exchanger 18 can be reduced.

  Accordingly, when the operation of the air mixing door 34 is controlled so that the blast air temperature TAV approaches the target blowing temperature TAO only in the cooling mode, the indoor condenser is not increased without increasing the flow rate of the circulating refrigerant circulating in the cycle. By increasing the pressure of the refrigerant at 12, the heating capability of the blower air in the indoor condenser 12 can be improved.

(C) Series dehumidification and heating mode In the series dehumidification and heating mode, the air conditioning controller 40 fully closes the first flow control valve 14a, fully opens the second flow control valve 14b, and throttles the third flow control valve 14c. Then, the fourth flow control valve 14d is set to the throttle state. Further, the air conditioning controller 40 opens the first on-off valve 17a, opens the second on-off valve 17b, closes the third on-off valve 17c, closes the fourth on-off valve 17d, and closes the fifth on-off valve 17e.

  Thereby, in the weak series dehumidifying and heating mode, as shown by the solid line arrow in FIG. 2, the compressor 11 → the indoor condenser 12 (→ the second flow control valve 14b → the ejector 15) → the accumulator 19 → the third flow control valve 14c. A refrigeration cycle in which the refrigerant circulates in the order of the outdoor heat exchanger 18 (→ the refrigerant passage 16a for dehumidifying and heating) → the fourth flow control valve 14d → the indoor evaporator 20 → the compressor 11 is constituted. For this reason, in the serial dehumidifying and heating mode, the outdoor heat exchanger 18 and the indoor evaporator 20 are connected in series to the refrigerant flow.

  With the configuration of the refrigerant circuit, the air-conditioning control device 40 determines the operation states of various control target devices (control signals to be output to various control target devices) based on the target blowout temperature TAO, detection signals of the sensor group, and the like.

  For example, the throttle opening of the third flow control valve 14c, that is, the control signal (control pulse) output to the third flow control valve 14c, is stored in the air conditioning control device 40 in advance based on the target outlet temperature TAO. Is determined with reference to the control map. Specifically, the throttle opening is determined to decrease as the target outlet temperature TAO increases. In other words, the throttle opening is determined to decrease with an increase in the heating capacity required for the cycle.

  Further, the throttle opening of the fourth flow control valve 14d is determined so that the degree of superheat of the suction refrigerant approaches the predetermined reference degree of superheat, as in the cooling mode. Therefore, the throttle opening of the fourth flow control valve 14d increases as the throttle opening of the third flow control valve 14a decreases. In other words, it is determined that the throttle opening increases as the heating capacity required for the cycle increases.

  In addition, the opening degree of the air mix door 34, that is, the control signal output to the electric actuator that drives the air mix door 34, is similar to the weak series dehumidifying and heating mode, and the blast air temperature detected by the conditioned air temperature sensor 47. TAV is determined so as to approach target outlet temperature TAO. The operating states of the other control target devices are determined in the same manner as in the cooling mode.

  Therefore, in the ejector refrigeration cycle 10 in the serial dehumidification heating mode, the state of the refrigerant changes as shown in the Mollier diagram of FIG.

  Specifically, in the in-line dehumidifying and heating mode, the air mix door 34 opens the blast air passage on the indoor condenser 12 side, so that the high-pressure refrigerant (point a8 in FIG. 8) discharged from the compressor 11 is supplied to the indoor condenser. 12 and exchanges heat with a part of the blown air cooled and dehumidified by the indoor evaporator 20 to radiate heat (point a8 → point e8 in FIG. 8). Thereby, a part of the blowing air is heated.

  The refrigerant flowing out of the indoor condenser 12 flows into the accumulator 19 via the first three-way joint 13a, the fully opened second flow control valve 14b, and the ejector 15, and is separated into gas and liquid. At this time, in the series dehumidifying and heating mode, the third flow rate control valve 14c and the fourth flow rate control valve 14d are connected in series, and both are in the throttle state, so that the refrigerant flowing through the nozzle portion 15a of the ejector 15 Is relatively slow. Therefore, the refrigerant is hardly depressurized in the nozzle portion 15a.

  The liquid-phase refrigerant separated by the accumulator 19 flows into the third flow control valve 14c and is decompressed (point e8 → point d8 in FIG. 8). The refrigerant decompressed by the third flow control valve 14c flows into the other refrigerant inlet / outlet of the outdoor heat exchanger 18.

  In the in-line dehumidification heating mode, the outdoor heat exchanger temperature Tout is lower than the outdoor temperature Tam, so the refrigerant flowing into the outdoor heat exchanger 18 is supplied from the outside air blown from the blower fan in the outdoor heat exchanger 18. It absorbs heat and evaporates (point d8 → point f8 in FIG. 8).

  The refrigerant flowing out from one refrigerant inlet / outlet of the outdoor heat exchanger 18 is subjected to the fourth flow rate adjustment through the third three-way joint 13c, the second three-way joint 13b, the dehumidifying / heating refrigerant passage 16a, and the fourth three-way joint 13d. The pressure is reduced by flowing into the valve 14d (point f8 → point g8 in FIG. 8). Subsequent operations are the same as in the cooling mode.

  Therefore, in the serial dehumidifying and heating mode, the air that has been cooled and dehumidified by the indoor evaporator 20 is reheated by the indoor condenser 12 and blown out into the vehicle cabin, whereby dehumidifying and heating the vehicle cabin can be performed. .

  Further, in the series dehumidifying and heating mode, the outdoor heat exchanger 18 functions as an evaporator, so that the heat release amount of the refrigerant in the indoor condenser 12 can be increased as compared with the weak series dehumidifying and heating mode. Thereby, the refrigerant pressure in the indoor condenser 12 can be increased without increasing the flow rate of the circulating refrigerant circulating through the cycle in the weak series dehumidification heating mode.

  As a result, the heating capability of the blown air in the indoor condenser 12 can be improved, and the blown air can be heated to a temperature zone higher than the weak series dehumidifying and heating mode.

  In the series dehumidification heating mode, the liquid-phase refrigerant flowing out of the liquid-phase refrigerant outlet of the accumulator 19 can flow into the outdoor heat exchanger 18. Therefore, the amount of heat absorbed by the refrigerant in the outdoor heat exchanger 18 can be increased as compared with the case where the refrigerant having a relatively high degree of dryness flows into the outdoor heat exchanger 18.

(D) Parallel dehumidification and heating mode In the parallel dehumidification and heating mode, the air conditioning control device 40 fully opens the first flow control valve 14a, sets the second flow control valve 14b to a throttled state, and sets the third flow control valve 14c to a throttled state. Then, the fourth flow control valve 14d is set to the throttle state. Further, the air conditioning controller 40 closes the first on-off valve 17a, opens the second on-off valve 17b, opens the third on-off valve 17c, opens the fourth on-off valve 17d, and closes the fifth on-off valve 17e.

  Thus, in the parallel dehumidifying and heating mode, the refrigerant circulates in the order of the compressor 11, the indoor condenser 12, the second flow control valve 14b, the ejector 15, the accumulator 19, and the compressor 11, as indicated by the solid arrow in FIG. At the same time, an ejector type refrigeration cycle in which the refrigerant circulates in the order of accumulator 19 → third flow control valve 14c → outdoor heat exchanger 18 → refrigerant suction port 15c of ejector 15 is configured.

  At the same time, a refrigeration cycle in which the refrigerant circulates in the order of the compressor 11 → the indoor condenser 12 (→ the first flow control valve 14a → the dehumidifying / heating refrigerant passage 16a) → the fourth flow control valve 14d → the indoor evaporator 20 → the compressor 11. Is configured. For this reason, in the parallel dehumidification heating mode, the outdoor heat exchanger 18 and the indoor evaporator 20 are connected in parallel to the refrigerant flow.

  With the configuration of the refrigerant circuit, the air-conditioning control device 40 determines the operation states of various control target devices (control signals to be output to various control target devices) based on the target blowout temperature TAO, the detection signals of the sensor group, and the like.

  For example, for the throttle opening of the second flow control valve 14b, that is, for the control signal (control pulse) output to the second flow control valve 14b, refer to the control map stored in the air conditioning control device 40 in advance. The flow rate of the refrigerant flowing from the first three-way joint 13a to the first flow control valve 14a side to the flow rate of the refrigerant flowing from the first three-way joint 13a to the second flow control valve 14b is a predetermined reference flow rate. It is determined to approach the ratio.

  The throttle opening of the third flow control valve 14c, that is, the control signal (control pulse) output to the third flow control valve 14c is stored in the air-conditioning control device 40 in advance based on the target outlet temperature TAO. Is determined with reference to the control map. Specifically, the throttle opening is determined to decrease as the target outlet temperature TAO increases. In other words, the throttle opening is determined to decrease with an increase in the heating capacity required for the cycle.

  Further, in the parallel dehumidifying and heating mode, the throttle opening of the third flow control valve 14c is determined such that the refrigerant evaporation temperature in the outdoor heat exchanger 18 is equal to or lower than the refrigerant evaporation temperature in the indoor evaporator 20.

  In addition, the opening degree of the air mix door 34, that is, the control signal output to the electric actuator that drives the air mix door 34, is similar to the weak series dehumidifying and heating mode, and the blast air temperature detected by the conditioned air temperature sensor 47. TAV is determined so as to approach target outlet temperature TAO. The operating states of the other control target devices are determined in the same manner as in the cooling mode.

  Therefore, in the ejector refrigeration cycle 10 in the parallel dehumidifying and heating mode, the state of the refrigerant changes as shown in the Mollier diagram of FIG.

  Specifically, in the parallel dehumidifying and heating mode, the air mix door 34 opens the blower air passage on the indoor condenser 12 side, so that the high-pressure refrigerant (point a9 in FIG. 9) discharged from the compressor 11 is supplied to the indoor condenser. 12 and exchanges heat with a part of the blown air cooled and dehumidified by the indoor evaporator 20 to radiate heat (point a9 → point b9 in FIG. 9). Thereby, a part of the blowing air is heated. The flow of the refrigerant flowing out of the indoor condenser 12 is branched at the first three-way joint 13a.

  One refrigerant branched at the first three-way joint 13a flows into the second flow control valve 14b and is decompressed (point b9 → point j9 in FIG. 9). The refrigerant decompressed by the second flow control valve 14b flows into the nozzle 15a of the ejector 15. The refrigerant flowing into the nozzle portion 15a is isentropically decompressed and injected (point j9 → point k9 in FIG. 9).

  Then, the refrigerant flowing out from one refrigerant inlet / outlet of the outdoor heat exchanger 18 is sucked from the refrigerant suction port 15c of the ejector 15 by the suction action of the injected refrigerant. The jet refrigerant injected from the nozzle portion 15a and the suction refrigerant sucked from the refrigerant suction port 15c flow into the diffuser portion 15d (k9 → m9 point, o9 point → m9 point in FIG. 9).

  In the diffuser section 15d, the velocity energy of the refrigerant is converted to pressure energy by expanding the refrigerant passage area. As a result, the pressure of the refrigerant mixture of the jet refrigerant and the suction refrigerant increases (point m9 → point n9 in FIG. 9). The refrigerant flowing out of the diffuser 15d flows into the accumulator 19 and is separated into gas and liquid.

  The liquid-phase refrigerant (point e9 in FIG. 9) separated by the accumulator 19 flows into the throttled third flow control valve 14c and is reduced in pressure (point e9 → point d9 in FIG. 9). The refrigerant decompressed by the third flow control valve 14c flows in from the other refrigerant inflow / outflow port of the outdoor heat exchanger 18, absorbs heat from the outside air blown from the blower fan, and evaporates (from point d9 to o9 in FIG. 9). point).

  The refrigerant flowing out of one refrigerant inlet / outlet of the outdoor heat exchanger 18 is sucked from the refrigerant suction port 15c of the ejector 15 via the third three-way joint 13c.

  Further, the other refrigerant branched at the first three-way joint 13a passes through the first flow control valve 14a, the second three-way joint 13b, the dehumidifying / heating refrigerant passage 16a, and the fourth three-way joint 13d which are fully opened. Then, it flows into the fourth flow control valve 14d and is decompressed (point b9 → point h9 in FIG. 9).

  The refrigerant decompressed by the fourth flow control valve 14d flows into the indoor evaporator 20, and exchanges heat with the air blown from the blower 32 and evaporates (point h9 → point g9 in FIG. 9). Thereby, the blown air is cooled. The refrigerant flowing out of the indoor evaporator 20 joins the gas-phase refrigerant separated by the accumulator 19 at the fifth three-way joint 13e, is sucked into the compressor 11, and is compressed again (point g9 in FIG. 9 →). a9 point).

  Therefore, in the parallel dehumidification and heating mode, the air that has been cooled and dehumidified by the indoor evaporator 20 is reheated by the indoor condenser 12 and blown out into the vehicle interior, whereby dehumidification and heating of the vehicle interior can be performed. .

  In the parallel dehumidifying and heating mode, the outdoor heat exchanger 18 and the indoor evaporator 20 are connected in parallel to the refrigerant flow as the entire cycle, and the outdoor heat exchanger 18 functions as an evaporator. Further, the refrigerant evaporation temperature in the outdoor heat exchanger 18 is lower than the refrigerant evaporation temperature in the indoor evaporator 20.

  Therefore, the amount of heat absorbed by the refrigerant from the outside air can be increased as compared with the serial dehumidifying and heating mode. Thereby, the refrigerant pressure in the indoor condenser 12 can be increased. As a result, the heating capacity of the blown air in the indoor condenser 12 can be improved, and the blown air can be heated to a higher temperature zone than in the serial dehumidifying and heating mode.

  In the parallel dehumidifying and heating mode, the refrigerant pressurized by the diffuser 15 d of the ejector 15 is combined with the refrigerant flowing out of the indoor evaporator 20 and is sucked into the compressor 11. Therefore, the power consumption of the compressor 11 can be reduced and the coefficient of performance (COP) of the cycle can be improved as compared with a normal refrigeration cycle apparatus without the ejector 15.

(E) Heating Mode In the heating mode, the air conditioning controller 40 closes the first flow control valve 14a, closes the second flow control valve 14b, and closes the third flow control valve 14c. Further, the air conditioning controller 40 closes the first on-off valve 17a, closes the second on-off valve 17b, opens the third on-off valve 17c, opens the fourth on-off valve 17d, and closes the fifth on-off valve 17e.

  Thereby, in the heating mode, the refrigerant circulates in the order of the compressor 11 → the indoor condenser 12 → the second flow control valve 14b → the ejector 15 → the accumulator 19 → the compressor 11, as shown by the solid arrow in FIG. An ejector refrigeration cycle in which the refrigerant circulates in the order of accumulator 19 → third flow control valve 14c → outdoor heat exchanger 18 → refrigerant suction port 15c of ejector 15 is configured.

  With the configuration of the refrigerant circuit, the air-conditioning control device 40 determines the operation states of various control target devices (control signals to be output to various control target devices) based on the target blowout temperature TAO, the detection signals of the sensor group, and the like.

  For example, the refrigerant discharge capacity of the compressor 11, that is, the control signal output to the electric motor of the compressor 11, is determined as follows. First, the target condenser temperature TCO of the indoor condenser 12 is determined with reference to a control map stored in the air conditioning control device 40 in advance based on the target outlet temperature TAO.

  Then, based on the deviation between the target condenser temperature TCO and the discharge refrigerant temperature Td detected by the discharge temperature sensor 45, compression is performed using a feedback control method so that the discharge refrigerant temperature Td approaches the target condenser temperature TCO. The control signal output to the electric motor of the machine 11 is determined.

  The throttle opening of the second flow control valve 14b, that is, the control signal (control pulse) output to the second flow control valve 14b, indicates the refrigerant discharge capacity of the compressor 11 (for example, the electric power of the compressor 11). Based on the control signal output to the motor), it is determined with reference to a control map stored in advance in the air conditioning control device 40.

  In this control map, the throttle opening of the second flow control valve 14b is determined such that the dryness x of the refrigerant flowing into the nozzle portion 15a is 0.5 or more and 0.8 or less. The range of the dryness x is a value experimentally obtained in advance as a value that can make the heating capacity of the blown air in the indoor condenser 12 close to the maximum value.

  The control signal output to the electric actuator that drives the air mix door 34 is determined so that the total flow rate of the blown air after passing through the indoor evaporator 20 flows through the air passage on the indoor condenser 12 side. The operating states of the other control target devices are determined in the same manner as in the parallel dehumidifying and heating mode.

  Therefore, in the ejector refrigeration cycle 10 in the heating mode, the state of the refrigerant changes as shown in the Mollier diagram in FIG.

  More specifically, in the heating mode, the air mix door 34 fully opens the blast air passage on the side of the indoor condenser 12, so that the high-pressure refrigerant (point a10 in FIG. 10) discharged from the compressor 11 12 and exchanges heat with the blast air to radiate heat (point a10 → point b10 in FIG. 10). Thereby, the blown air is heated.

  The refrigerant flowing out of the indoor condenser 12 flows into the second flow control valve 14b via the first three-way joint 13a and is decompressed (point b10 → point j10 in FIG. 10). Thereby, the dryness x of the refrigerant flowing into the nozzle portion 15a is adjusted to 0.5 or more and 0.8 or less.

  The refrigerant decompressed by the second flow control valve 14b flows into the nozzle 15a of the ejector 15. The refrigerant that has flowed into the nozzle 15a is isentropically reduced in pressure and injected (point j10 → point k10 in FIG. 10).

  Then, the refrigerant flowing out from one refrigerant inlet / outlet of the outdoor heat exchanger 18 is sucked from the refrigerant suction port 15c of the ejector 15 by the suction action of the injected refrigerant. The refrigerant injected from the nozzle 15a and the refrigerant sucked from the refrigerant suction port 15c flow into the diffuser 15d (k10 → m10, o10 → m10 in FIG. 10).

  In the diffuser section 15d, the velocity energy of the refrigerant is converted to pressure energy by expanding the refrigerant passage area. Thereby, the pressure of the mixed refrigerant of the injection refrigerant and the suction refrigerant increases (point m10 → point n10 in FIG. 10). The refrigerant flowing out of the diffuser 15d flows into the accumulator 19 and is separated into gas and liquid.

  The liquid-phase refrigerant (point e10 in FIG. 10) separated by the accumulator 19 flows into the throttled third flow control valve 14c and is reduced in pressure (point e10 → point d10 in FIG. 10). The refrigerant decompressed by the third flow control valve 14c flows in from the other refrigerant inflow / outflow port of the outdoor heat exchanger 18, absorbs heat from the outside air blown from the blower fan, and evaporates (from point d10 to o10 in FIG. 10). point).

  The refrigerant flowing out of one refrigerant inlet / outlet of the outdoor heat exchanger 18 is sucked from the refrigerant suction port 15c of the ejector 15 via the third three-way joint 13c. Therefore, the refrigerant flow direction in the outdoor heat exchanger 18 in the heating mode is different from the refrigerant flow direction in the outdoor heat exchanger 18 in the cooling mode.

  The liquid-phase refrigerant (point f10 in FIG. 10) separated by the accumulator 19 is sucked into the compressor 11 via the fifth three-way joint 13e and compressed again (point f9 → point a9 in FIG. 10).

  Therefore, in the heating mode, the inside of the vehicle compartment can be heated by blowing the blast air heated by the indoor condenser 12 into the vehicle compartment.

  Further, in the heating mode, the refrigerant pressurized by the diffuser 15 d of the ejector 15 is sucked into the compressor 11. Therefore, the consumption of the compressor 11 is lower than that of a normal refrigeration cycle device in which the refrigerant evaporation pressure in the heat exchanger functioning as an evaporator (in the heating mode, the outdoor heat exchanger 18) is equal to the pressure of the refrigerant sucked into the compressor 11. Power can be reduced and COP can be improved.

  As described above, according to the ejector refrigeration cycle 10 of the present embodiment, in the vehicle air conditioner 1, the operation in the cooling mode, the heating mode, the weak series dehumidification heating mode, the series dehumidification heating mode, and the parallel dehumidification heating mode is performed. By switching, appropriate air conditioning in the vehicle interior can be realized.

  Furthermore, in the ejector-type refrigeration cycle 10 of the present embodiment, the temperature adjustment range of the blast air at the time of dehumidifying and heating in the vehicle compartment can be expanded.

  This will be described in more detail. In the prior art ejector refrigeration cycle, when performing outdoor heating and dehumidifying heating by connecting an outdoor heat exchanger and an indoor evaporator in series with the refrigerant flow, in order to properly operate the ejector refrigeration cycle, It was necessary to maintain the refrigerant pressure in the outdoor heat exchanger at or above a predetermined value. For this reason, there has been a range in which the temperature of the blown air (blow-out air temperature) blown into the vehicle interior during dehumidifying heating cannot be adjusted.

  Specifically, in the ejector refrigeration cycle of the related art, when the outdoor heat exchanger and the indoor evaporator are switched to the refrigerant circuit that connects the refrigerant flow in series with respect to the refrigerant flow, the refrigerant flows within the range A in FIG. The outlet air temperature could be adjusted. In addition, when the outdoor heat exchanger and the indoor evaporator were switched to a refrigerant circuit that connected in parallel to the refrigerant flow, the temperature of the blown air could be adjusted within the range C in FIG.

  In other words, in the ejector-type refrigeration cycle of the related art, the blown air temperature could not be adjusted within the range B of FIG.

  On the other hand, in the ejector refrigeration cycle 10 of the present embodiment, even when the refrigerant pressure in the outdoor heat exchanger 18 is reduced to be equal to the refrigerant evaporation pressure in the indoor evaporator 20 in the serial dehumidification heating mode, The type refrigeration cycle 10 can be operated appropriately. Thereby, in the series dehumidifying heating mode of the present embodiment, the temperature of the blown air can be adjusted within the range B in FIG.

  Further, in the ejector type refrigeration cycle 10 of the present embodiment, in the weak series dehumidifying and heating mode, the blow-out air temperature can be adjusted mainly in the range A of FIG. The temperature of the blown air can be adjusted within the range C. Therefore, the temperature adjustment range of the blown air blown into the vehicle compartment at the time of dehumidifying and heating can be expanded as compared with the conventional ejector refrigeration cycle.

  In the ejector refrigeration cycle 10 of the present embodiment, the flow direction of the refrigerant in the outdoor heat exchanger in the heating mode and the flow direction of the refrigerant in the cooling mode are reversed. Further, the passage cross-sectional area of the refrigerant passage formed inside the outdoor heat exchanger 18 is changed from the refrigerant inlet (the other refrigerant inflow / outlet) side to the refrigerant outlet (the one refrigerant inflow / outlet) side in the heating mode. It is expanding.

  According to this, the pressure loss of the refrigerant flowing through the outdoor heat exchanger 18 can be reduced, and the COP can be further improved.

  More specifically, the outdoor heat exchanger 18 in the heating mode functions as an evaporator. Therefore, in the refrigerant passage in the outdoor heat exchanger 18, the liquid-phase refrigerant evaporates from the refrigerant inlet side to the refrigerant outlet side, so that the density of the refrigerant decreases. Accordingly, the pressure loss of the refrigerant flowing through the outdoor heat exchanger 18 can be reduced by increasing the cross-sectional area of the refrigerant passage from the refrigerant inlet side to the refrigerant outlet side of the outdoor heat exchanger 18.

  On the other hand, the outdoor heat exchanger 18 in the cooling mode functions as a radiator. Therefore, in the refrigerant passage in the outdoor heat exchanger 18, the density of the refrigerant increases because the gas-phase refrigerant condenses from the refrigerant inlet side to the refrigerant outlet side. Therefore, even if the cross-sectional area of the refrigerant passage decreases from the refrigerant inlet side to the refrigerant outlet side of the outdoor heat exchanger 18, the pressure loss of the refrigerant flowing through the outdoor heat exchanger 18 may increase. Absent.

  Here, in the present embodiment, the refrigerant flow in the outdoor heat exchanger 18 is in the same direction as in the heating mode also in the series dehumidification heating mode and the parallel dehumidification heating mode in which the outdoor heat exchanger 18 functions as an evaporator. Therefore, the pressure loss of the refrigerant flowing through the outdoor heat exchanger 18 can be reduced also in the series dehumidification heating mode and the parallel dehumidification heating mode.

  Also, in the weak series dehumidification heating mode in which the outdoor heat exchanger 18 functions as a radiator, the refrigerant flow in the outdoor heat exchanger 18 is in the same direction as in the cooling mode. Therefore, even in the weak series dehumidification heating mode, the pressure loss of the refrigerant flowing through the outdoor heat exchanger 18 does not increase.

  In other words, in the ejector refrigeration cycle 10 of the present embodiment, the flow direction of the refrigerant in the outdoor heat exchanger 18 when the outdoor heat exchanger 18 functions as an evaporator, and the outdoor heat exchanger 18 functions as a radiator. The flow direction of the refrigerant in the outdoor heat exchanger 18 at the time is different, and the refrigerant passage formed inside the outdoor heat exchanger 18 is connected to the refrigerant inlet side when the outdoor heat exchanger 18 functions as an evaporator. The cross-sectional area of the passage increases toward the outlet side.

(2nd Embodiment)
In this embodiment, as shown in FIGS. 12 to 14, an ejector refrigeration cycle 10a in which the cycle configuration is changed from the ejector refrigeration cycle 10 of the first embodiment will be described. 12 to 14, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals. This is the same in the following drawings.

  More specifically, in the ejector-type refrigeration cycle 10a, the refrigerant flowing out of the indoor condenser 12 bypasses the ejector 15, the outdoor heat exchanger 18, and the like, and is directed to the fourth flow control valve 14d serving as the second pressure reducing means. A bypass passage 16b leading to the air passage is added. For this reason, the sixth three-way joint 13f is arranged in a refrigerant passage extending from the refrigerant outlet side of the indoor condenser 12 to the refrigerant inlet of the first three-way joint 13a.

One refrigerant outlet of the fourth three-way joint 13d is connected to one refrigerant outlet of the sixth three-way joint 13f via a bypass passage 16b. The inlet side of the first flow control valve 14a is connected to the other refrigerant outlet of the sixth three-way joint 13f via the first three-way joint 13a. The first three-way joint 13 a of the present embodiment is a heating-side branch portion, the first flow control valve 14a is a third decompressor.

  A sixth on-off valve 17f having the same configuration as the second on-off valve 17b and the like is arranged in the bypass passage 16b. Further, the second three-way joint 13b of the present embodiment is disposed in a refrigerant passage connecting the outdoor heat exchanger 18 and the third flow control valve 14c. For this reason, the refrigerant passage 16a for dehumidifying and heating of the present embodiment connects the refrigerant inflow / outflow port on the third flow rate control valve 14c side of the outdoor heat exchanger 18 to the inlet of the fourth flow rate control valve 14d as the second decompression device. are doing. Further, in the present embodiment, the first opening / closing section 17a is omitted.

  The accumulator 19 of the present embodiment has a gas-phase refrigerant outlet for letting out the separated gas-phase refrigerant, and a gas-phase refrigerant inlet for letting out the gas-phase refrigerant that has flowed out of the indoor evaporator 20. Is provided. The other liquid-phase refrigerant outlets described in the first embodiment and the fourth and fifth on-off valves 17d and 17e connected to each liquid-phase refrigerant outlet are eliminated.

  Further, the gas-phase refrigerant outlet of the accumulator 19 of the present embodiment is directly connected to the suction port side of the compressor 11 without going through a three-way joint or the like. Other configurations of the ejector refrigeration cycle 10a are the same as those of the ejector refrigeration cycle 10 described in the first embodiment.

  Next, the operation of the present embodiment in the above configuration will be described. In the ejector refrigeration cycle 10a of the present embodiment, the operation in the cooling mode, the series dehumidifying / heating mode, the parallel dehumidifying / heating mode, and the heating mode can be switched. The operation in the cooling mode, the parallel dehumidifying / heating mode, and the heating mode is switched in the same manner as in the first embodiment.

  Further, in the operation in the series dehumidifying and heating mode, the target outlet temperature TAO is equal to or higher than the cooling reference temperature α in a state where the cooling switch is turned on regardless of the outdoor heat exchanger temperature Tout, and the outside air temperature Tam is determined in advance. This is executed when the temperature is higher than the dehumidifying heating reference temperature β. The operation in each operation mode will be described below.

(A) Cooling mode In the cooling mode, the air-conditioning control device 40 fully opens the first flow control valve 14a, fully closes the second flow control valve 14b, fully closes the third flow control valve 14c, and sets the fourth flow rate. The regulating valve 14d is set in the throttled state. Further, the air conditioning controller 40 opens the second on-off valve 17b, closes the third on-off valve 17c, and closes the sixth on-off valve 17f.

  Thereby, in the cooling mode, as shown by a solid line arrow in FIG. 12, the compressor 11 → the indoor condenser 12 (→ the first flow control valve 14a) → the outdoor heat exchanger 18 (→ the dehumidifying and heating refrigerant passage 16a) → A refrigeration cycle in which the refrigerant circulates in the order of the fourth flow control valve 14d → the indoor evaporator 20 → the accumulator 19 → the compressor 11 is configured.

  With the configuration of the refrigerant circuit, the air-conditioning control device 40 determines the operation states of various control target devices (control signals to be output to various control target devices) based on the target blowout temperature TAO, the detection signals of the sensor group, and the like.

  For example, the throttle opening of the fourth flow control valve 14d, that is, the control signal (control pulse) output to the fourth flow control valve 14d is determined so that the COP of the ejector refrigeration cycle 10a approaches a local maximum value. . The operating states of the other control target devices are determined in the same manner as in the first embodiment.

  Accordingly, the ejector refrigeration cycle 10a in the cooling mode operates substantially in the same manner as the cooling mode of the first embodiment, and blows out the blast air cooled by the indoor evaporator 20 into the vehicle interior to thereby improve the vehicle interior. Cooling can be performed.

  Further, the ejector refrigeration cycle 10a has a cycle configuration in which the gas-phase refrigerant separated by the accumulator 19 is sucked into the compressor 11, so that the problem of liquid compression of the compressor 11 can be avoided.

(B) Series dehumidification and heating mode In the series dehumidification and heating mode, the air conditioning controller 40 closes the first flow control valve 14a, fully closes the second flow control valve 14b, and fully closes the third flow control valve 14c. And the fourth flow control valve 14d is set in the throttled state. Further, the air conditioning controller 40 opens the second on-off valve 17b, closes the third on-off valve 17c, and closes the sixth on-off valve 17f.

  Accordingly, in the cooling mode, as shown by the solid line arrow in FIG. 12, the compressor 11 → the indoor condenser 12 → the first flow control valve 14a → the outdoor heat exchanger 18 (→ the dehumidifying / heating refrigerant passage 16a) → the fourth. A refrigeration cycle in which the refrigerant circulates in the same order as in the cooling mode of the compressor 11 is constituted by the flow control valve 14d → the indoor evaporator 20 → the accumulator 19 →. For this reason, in the serial dehumidifying and heating mode, the outdoor heat exchanger 18 and the indoor evaporator 20 are connected in series to the refrigerant flow.

  With the configuration of the refrigerant circuit, the air-conditioning control device 40 determines the operation states of various control target devices (control signals to be output to various control target devices) based on the target blowout temperature TAO, the detection signals of the sensor group, and the like.

  For example, the throttle opening of the first flow control valve 14a, that is, the control signal (control pulse) output to the first flow control valve 14a is stored in the air conditioning control device 40 in advance based on the target outlet temperature TAO. It is determined with reference to the control map. Specifically, the throttle opening is determined to decrease as the target outlet temperature TAO increases. In other words, the throttle opening is determined to decrease with an increase in the heating capacity required for the cycle.

  The throttle opening of the fourth flow control valve 14d is determined so that the COP of the ejector refrigeration cycle 10a approaches the maximum value, as in the cooling mode. Therefore, the throttle opening of the fourth flow control valve 14d increases as the throttle opening of the first flow control valve 14a decreases. In other words, it is determined that the throttle opening increases as the heating capacity required for the cycle increases. The operating states of the other control target devices are determined in the same manner as in the first embodiment.

  Therefore, in the ejector refrigeration cycle 10a in the series dehumidifying and heating mode, when the outdoor heat exchanger temperature Tout is higher than the outdoor temperature Tam, the outdoor heat exchanger 18 functions as a radiator for releasing the refrigerant. .

  For this reason, when the outdoor heat exchanger temperature Tout is higher than the outdoor temperature Tam, it operates substantially in the same manner as in the weak series dehumidifying and heating mode of the first embodiment, and is cooled by the indoor evaporator 20. The dehumidified blast air is reheated in the indoor condenser 12 and blown out into the vehicle interior, whereby dehumidification and heating in the vehicle interior can be performed.

  On the other hand, in the ejector refrigeration cycle 10a in the series dehumidifying and heating mode, when the outdoor heat exchanger temperature Tout is lower than the outdoor temperature Tam, the outdoor heat exchanger 18 functions as an evaporator for evaporating the refrigerant. .

  For this reason, when the outdoor heat exchanger temperature Tout is lower than the outdoor temperature Tam, it operates substantially in the same manner as in the series dehumidification heating mode of the first embodiment, and is cooled by the indoor evaporator 20. The dehumidified blast air is reheated by the indoor condenser 12 and blown out into the vehicle interior, whereby dehumidification and heating of the vehicle interior can be performed.

  Further, similarly to the weak series dehumidification heating mode and the series dehumidification heating mode of the first embodiment, when the outdoor heat exchanger temperature Tout is lower than the outside air temperature Tam, the outdoor heat exchanger temperature Tout becomes the outside air temperature. It is possible to improve the heating capability of the blown air in the indoor condenser 12 and raise the temperature of the blown air to a high temperature zone, as compared with the case where the temperature is higher than Tam.

(C) Parallel dehumidification / heating mode In the parallel dehumidification / heating mode, the air conditioning controller 40 closes the first flow control valve 14a, closes the second flow control valve 14b, and closes the third flow control valve 14c. And the fourth flow control valve 14d is set in the throttled state. Further, the air conditioning control device 40 closes the second on-off valve 17b, opens the third on-off valve 17c, and opens the sixth on-off valve 17f.

  Thereby, in the parallel dehumidification heating mode, the refrigerant circulates in the order of the compressor 11, the indoor condenser 12, the second flow control valve 14b, the ejector 15, the accumulator 19, and the compressor 11, as indicated by the solid arrow in FIG. At the same time, an ejector type refrigeration cycle in which the refrigerant circulates in the order of accumulator 19 → third flow control valve 14c → outdoor heat exchanger 18 → refrigerant suction port 15c of ejector 15 is configured.

  At the same time, a refrigeration cycle is formed in which the refrigerant circulates in the order of the compressor 11 → the indoor condenser 12 (→ the bypass passage 16b) → the fourth flow control valve 14d → the indoor evaporator 20 → the compressor 11. For this reason, in the parallel dehumidification heating mode, the outdoor heat exchanger 18 and the indoor evaporator 20 are connected in parallel to the refrigerant flow.

  With the configuration of the refrigerant circuit, the air-conditioning control device 40 operates the various control target devices based on the target blowing temperature TAO, the detection signal of the sensor group, and the like (similar to the parallel dehumidifying and heating mode of the first embodiment). Control signal to be output to the control target device).

  Therefore, the ejector refrigeration cycle 10a in the parallel dehumidifying and heating mode operates substantially in the same manner as in the parallel dehumidifying and heating mode of the first embodiment, and the blast air cooled and dehumidified by the indoor evaporator 20 is condensed in the room. By reheating in the heater 12 and blowing it out into the vehicle interior, dehumidification and heating in the vehicle interior can be performed.

  Further, similarly to the parallel dehumidifying and heating mode of the first embodiment, the amount of heat absorbed by the refrigerant from the outside air can be increased as compared with the serial dehumidifying and heating mode. As a result, the heating capacity of the blown air in the indoor condenser 12 can be improved, and the blown air can be heated to a higher temperature zone than in the serial dehumidifying and heating mode.

(D) Heating Mode In the parallel dehumidifying and heating mode, the air-conditioning control device 40 closes the first flow control valve 14a, closes the second flow control valve 14b, and closes the third flow control valve 14c. . Further, the air conditioning control device 40 closes the second on-off valve 17b, opens the third on-off valve 17c, and closes the sixth on-off valve 17f.

  Thereby, in the heating mode, the refrigerant circulates in the order of the compressor 11 → the indoor condenser 12 → the second flow control valve 14b → the ejector 15 → the accumulator 19 → the compressor 11 as shown by the solid arrow in FIG. An ejector refrigeration cycle in which the refrigerant circulates in the order of accumulator 19 → third flow control valve 14c → outdoor heat exchanger 18 → refrigerant suction port 15c of ejector 15 is configured.

  The air-conditioning control device 40 has the configuration of the refrigerant circuit and operates the various control target devices (various control targets) based on the target blow-out temperature TAO, the detection signal of the sensor group, and the like, as in the heating mode of the first embodiment. Control signal to be output to the device).

  Accordingly, the ejector refrigeration cycle 10a in the cooling mode operates substantially in the same manner as in the heating mode of the first embodiment, and blows out the blast air heated by the indoor condenser 12 into the vehicle interior to thereby improve the vehicle interior. Heating can be performed. Further, in the heating mode, the COP can be improved as in the first embodiment.

  As described above, according to the ejector refrigeration cycle 10a of the present embodiment, in the vehicle air conditioner 1, the operation is switched to the cooling mode, the heating mode, the series dehumidifying / heating mode, and the parallel dehumidifying / heating mode, so that the vehicle interior Suitable air conditioning can be realized.

  Furthermore, in the ejector refrigeration cycle 10 a of the present embodiment, the refrigerant pressure in the outdoor heat exchanger 18 can be reduced until it becomes equal to the refrigerant evaporation pressure in the indoor evaporator 20 in the serial dehumidification and heating mode. Therefore, similarly to the first embodiment, the temperature adjustment range of the blown air blown into the vehicle interior during dehumidifying and heating can be expanded.

  In the ejector refrigeration cycle 10a of the present embodiment, the flow direction of the refrigerant in the outdoor heat exchanger in the heating mode and the flow direction of the refrigerant in the cooling mode are reversed. Therefore, similarly to the first embodiment, the pressure loss of the refrigerant flowing through the outdoor heat exchanger 18 can be reduced in the heating mode, and the pressure loss of the refrigerant flowing through the outdoor heat exchanger 18 can be reduced in the cooling mode. There is no increase.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention.

  (1) In the above-described embodiment, an example in which the ejector refrigeration cycle 10, 10a according to the present invention is applied to an air conditioner for an electric vehicle has been described, but the application of the ejector refrigeration cycle 10, 10a is not limited thereto. . For example, the present invention may be applied to an air conditioner for a normal vehicle that obtains a driving force for vehicle traveling from an internal combustion engine (engine) or a hybrid vehicle that obtains a driving force for vehicle traveling from both an internal combustion engine and an electric motor for traveling. Good.

  When the invention is applied to a vehicle having an internal combustion engine, the vehicle air conditioner 1 may be provided with a heater core for heating the blast air using the cooling water of the internal combustion engine as a heat source as an auxiliary heating means for the blast air. Further, the present invention may be applied to a stationary air conditioner without being limited to a vehicle.

  Further, in the above-described embodiment, the ejector refrigeration cycle in which the refrigerant discharged from the compressor 11 and the blast air are heat-exchanged in the indoor condenser 12 to directly heat the blast air using the refrigerant discharged from the compressor 11 as a heat source. Although description has been made of the case of No. 10, the heating mode of the blown air in the indoor condenser 12 is not limited to this.

  For example, a heat medium circulation circuit for circulating a heat medium is provided, and the indoor radiator is configured as a water-refrigerant heat exchanger for exchanging heat between the refrigerant discharged from the compressor and the heat medium. A heating heat exchanger for heating the blown air by exchanging heat between the heat medium heated by and the blown air may be arranged. That is, the indoor radiator may use the refrigerant discharged from the compressor (the high-pressure side refrigerant in the cycle) as a heat source to indirectly heat the blast air via the heat medium.

  Further, when the present invention is applied to a vehicle having an internal combustion engine, the cooling water of the internal combustion engine may be used as a heat medium to flow through the heat medium circulation circuit. Further, in an electric vehicle, cooling water for cooling a battery or electric equipment may be used as a heat medium to flow through a heat medium circulation circuit.

  (2) Each component of the ejector refrigeration cycle 10, 10a is not limited to the one disclosed in the above-described embodiment.

  For example, in the above-described embodiment, an example has been described in which an electric compressor is employed as the compressor 11, but the compressor 11 is not limited to this. For example, the compressor 11 may be an engine-driven variable displacement compressor or the like.

  Further, in the above-described embodiment, an example has been described in which the blown air is heated by exchanging heat between the high-pressure refrigerant and the blown air in the indoor condenser 12, but instead of the indoor condenser 12, for example, a heat medium may be used. Providing a heat medium circulation circuit for circulation, a water-refrigerant heat exchanger for exchanging heat between the high-pressure refrigerant and the heat medium in this heat medium circulation circuit, and a heat medium heated by the water-refrigerant heat exchanger and blast air. May be provided with a heating heat exchanger or the like for exchanging heat with the air to heat the blown air.

  Further, in the above-described embodiment, an example has been described in which a plurality of flow control valves and on-off valves are employed as the refrigerant circuit switching device, but the refrigerant circuit switching device is not limited to this. If at least the above-described heating mode refrigerant circuit and the series dehumidification heating mode refrigerant circuit can be switched, for example, a combination of a flow control valve and an open / close valve that does not have a fully closed function, a four-way valve, or the like is adopted. You may.

  In addition, an apparatus in which the components described in the above embodiment are integrated may be employed. For example, the second flow control valve 14b, the ejector 15, the accumulator 19, and the like may be integrated (moduleed). In this case, a needle-like or conical valve body is disposed in the passage of the nozzle portion 15a of the ejector 15, and by displacing the valve body, the same function as the second flow rate regulating valve 14b is exerted. It may be.

  Further, on the refrigerant outlet side of the indoor evaporator 20 of each of the ejector type refrigeration cycles 10 and 10a of the above-described embodiments, an evaporation pressure adjusting valve for setting the refrigerant evaporation pressure of the indoor evaporator 20 to a predetermined value or more is arranged. You may. According to this, frost formation on the indoor evaporator 20 can be more reliably prevented by the mechanical mechanism.

  Further, in the above embodiment, an example in which R134a is adopted as the refrigerant has been described, but the refrigerant is not limited to this. For example, R1234yf, R600a, R410A, R404A, R32, R407C, etc. may be adopted. Alternatively, a mixed refrigerant obtained by mixing a plurality of types of these refrigerants may be employed.

(3) In the heating mode of the above-described embodiments, an example has been described that adjusts the valve opening degree of the second flow regulating valve 14b based on the refrigerant discharge capacity of the compressor 11, the second flow regulating valve 14b The adjustment of the valve opening is not limited to this.

For example, a dryness sensor for detecting the dryness of the refrigerant on the outlet side of the indoor condenser 12 is provided, and the valve of the second flow control valve 14b is controlled so that the detection value of the dryness sensor is 0.5 or more and 0.8 or less. it may adjust the degree of opening. Further, the valve opening of the second flow control valve 14b may be adjusted so that the COP of the ejector type refrigeration cycle 10, 10a approaches the maximum value.

  (4) In the above-described embodiment, an example in which each operation mode is switched by executing the air conditioning control program has been described. However, switching of each operation mode is not limited to this. For example, an operation mode setting switch for setting each operation mode may be provided on the operation panel 50, and each heating mode may be switched according to an operation signal of the operation mode setting switch.

11 Compressor 12 Indoor condenser (heat exchanger for heating)
13 a first three-way joint (heating-side branch portion)
14a First flow control valve (third pressure reducing device)
14c Third flow control valve (first pressure reducing device)
14d fourth flow control valve (second pressure reducing device)
15 Ejectors 17a to 17f First to sixth on-off valves (refrigerant circuit switching device)
18 outdoor heat exchanger 19 accumulator 20 indoor evaporator (cooling heat exchanger)

Claims (6)

An ejector refrigeration cycle applied to an air conditioner,
A compressor (11) for compressing and discharging the refrigerant;
A heating heat exchanger (12) for heating the blown air blown into the air-conditioned space using the high-pressure refrigerant discharged from the compressor as a heat source;
The refrigerant sucked from the refrigerant suction port (15c) by the suction action of the injected refrigerant injected from the nozzle part (15a) for reducing the pressure of the refrigerant flowing out of the heating heat exchanger, and is sucked from the injected refrigerant and the refrigerant suction port. An ejector (15) having a pressure increasing section (15d) for increasing the pressure of the mixed refrigerant with the drawn suction refrigerant;
A gas-liquid separator (19) for separating gas-liquid of the refrigerant flowing out of the ejector;
A first pressure reducing device (14c) for reducing the pressure of the liquid-phase refrigerant flowing out of the gas-liquid separator;
An outdoor heat exchanger (18) for exchanging heat between the refrigerant and outside air;
A cooling heat exchanger (20) for evaporating a refrigerant and cooling the blast air before passing through the heating heat exchanger;
A second decompression device (14d) for decompressing the refrigerant flowing into the cooling heat exchanger;
A refrigerant circuit switching device (17a to 17e) for switching the refrigerant circuit,
The refrigerant circuit switching device,
In the heating mode in which the blast air is heated, the liquid-phase refrigerant separated by the gas-liquid separator flows into the outdoor heat exchanger through the first pressure reducing device, and the refrigerant flows out of the outdoor heat exchanger. While flowing into the refrigerant suction port, switching to a refrigerant circuit for sucking the gas-phase refrigerant separated by the gas-liquid separator into the compressor,
Series dehumidifying and heating mode, the gas-liquid separator of the liquid-phase refrigerant wherein the refrigerant flowing out of the outlet first reheating the feed air is cooled by the cooling heat exchanger in the heating heat exchanger The refrigerant flows into the outdoor heat exchanger via a pressure reducing device, and the refrigerant flowing out of the outdoor heat exchanger flows into the cooling heat exchanger via the second pressure reducing device, and flows out from the cooling heat exchanger. An ejector-type refrigeration cycle that switches to a refrigerant circuit that causes the compressed refrigerant to be sucked into the compressor. An ejector refrigeration cycle applied to an air conditioner,
A compressor (11) for compressing and discharging the refrigerant;
A heating heat exchanger (12) for heating the blown air blown into the air-conditioned space using the high-pressure refrigerant discharged from the compressor as a heat source;
A heating-side branch portion ( 13a ) for branching the flow of the refrigerant flowing out of the heating heat exchanger;
The refrigerant is sucked from the refrigerant suction port (15c) by the suction effect of the injected refrigerant injected from the nozzle portion (15a) for reducing the pressure of one of the refrigerants branched at the heating-side branch portion. An ejector (15) having a pressure increasing section (15d) for increasing the pressure of a refrigerant mixture with the suction refrigerant sucked from the mouth;
A gas-liquid separator (19) for separating gas-liquid of the refrigerant flowing out of the ejector;
A first pressure reducing device (14c) for reducing the pressure of the liquid-phase refrigerant flowing out of the gas-liquid separator;
An outdoor heat exchanger (18) for exchanging heat between the refrigerant and outside air;
A cooling heat exchanger (20) for evaporating a refrigerant and cooling the blast air before passing through the heating heat exchanger;
A second decompression device (14d) for decompressing the refrigerant flowing into the cooling heat exchanger;
A third decompression device (14a) for decompressing the other refrigerant branched at the heating-side branch portion;
A refrigerant circuit switching device (17b to 17f) for switching a refrigerant circuit,
The refrigerant circuit switching device,
In the heating mode for heating the blast air, the liquid-phase refrigerant separated by the gas-liquid separator flows into the outdoor heat exchanger via the first pressure reducing device, and the refrigerant flows out of the outdoor heat exchanger. While flowing into the refrigerant suction port, switched to a refrigerant circuit that sucks the gas-phase refrigerant separated by the gas-liquid separator into the compressor,
Wherein the blowing air cooled by the cooling heat exchanger reheating series dehumidification and heating mode in the heating heat exchanger, the refrigerant flowing out of the heating heat exchanger via a third decompressor The refrigerant flowing into the outdoor heat exchanger, the refrigerant flowing out of the outdoor heat exchanger flows into the cooling heat exchanger via a second decompression device, and the refrigerant flowing out of the cooling heat exchanger is vapor-liquid An ejector refrigeration cycle that switches to a refrigerant circuit that flows into a separator and causes the gas-phase refrigerant separated by the gas-liquid separator to be sucked into the compressor. A refrigerant passage (16a) for dehumidifying and heating that guides the refrigerant flowing out of the outdoor heat exchanger to the inlet side of the second decompression device in the serial dehumidifying and heating mode ;
The refrigerant circuit switching device has a dehumidifying and heating on-off valve (17b) for opening and closing the dehumidifying and heating refrigerant passage,
The ejector refrigeration cycle according to claim 1, wherein the on-off valve for dehumidifying and heating closes the refrigerant passage for dehumidifying and heating in the heating mode, and opens the refrigerant passage for dehumidifying and heating in the in-line dehumidifying and heating mode. . The refrigerant circuit switching device,
Wherein the blowing air cooled by the cooling heat exchanger in a parallel dehumidifying heating mode to reheat a higher heating capacity than the series dehumidification and heating mode in the heating heat exchanger, from the heating heat exchanger The flow of the outflowing refrigerant is branched, one of the branched refrigerants flows into the nozzle portion, and the liquid-phase refrigerant separated by the gas-liquid separator is passed through the first decompression device to the outdoor heat exchanger. And the refrigerant flowing out of the outdoor heat exchanger flows into the refrigerant suction port, and the gas-phase refrigerant separated by the gas-liquid separator is sucked into the compressor. The refrigerant circuit according to any one of claims 1 to 3, wherein the refrigerant circuit is switched to a refrigerant circuit that causes the refrigerant to flow into the cooling heat exchanger via the second decompression device and causes the refrigerant flowing out of the cooling heat exchanger to be sucked into the compressor. Eje described in one Data type refrigeration cycle. The refrigerant circuit switching device,
In the cooling mode for cooling the blown air, the refrigerant flowing out of the heating heat exchanger flows into the outdoor heat exchanger, and the refrigerant flowing out of the outdoor heat exchanger is cooled through the second decompression device. The ejector-type refrigeration cycle according to any one of claims 1 to 4, wherein the refrigerant circuit is switched to a refrigerant circuit that causes the refrigerant to flow into the heat exchanger and flow out of the cooling heat exchanger into the compressor. The flow direction of the refrigerant in the outdoor heat exchanger in the heating mode and the flow direction of the refrigerant in the outdoor heat exchanger in the cooling mode are different,
The ejector refrigeration cycle according to claim 5, wherein the refrigerant passage formed inside the outdoor heat exchanger has a passage cross-sectional area that increases from a refrigerant inlet side to a refrigerant outlet side in the heating mode. .

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