WO2017221618A1 - Ejector refrigeration cycle - Google Patents

Abstract

An ejector refrigeration cycle comprises a compressor (11), a heat exchanger for heating (12), a first pressure reducing device (15b), an outdoor heat exchanger (17), a second pressure reducing device (15e), a heat exchanger for cooling (21), an ejector (16), a gas-liquid separator (19), and a refrigerant circuit switching device (13a, 13b, 18a, 18b). The refrigerant circuit switching device causes refrigerant flowing from the heat exchanger for heating to flow, in order, to the first pressure reducing device, the outdoor heat exchanger, the second pressure reducing device, the heat exchanger for cooling, and the compressor in a first dehumidification heating mode, and to flow, in order, to the second pressure reducing device, the heat exchanger for cooling, the first pressure reducing device, the outdoor heat exchanger, and the compressor in a second dehumidification heating mode. The direction that the refrigerant flows in the outdoor heat exchanger while in the first dehumidification heating mode is the same direction that the refrigerant flows in the outdoor heat exchanger while in the second dehumidification heating mode. The direction that the refrigerant flows in the outdoor heat exchanger while in the first dehumidification heating mode is opposite to the direction that the refrigerant flows in the outdoor heat exchanger while in a heating mode.

Description

Ejector refrigeration cycle Cross-reference of related applications

This application is based on Japanese Patent Application No. 2016-122859 filed on June 21, 2016, the disclosure of which is incorporated herein by reference.

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

Conventionally, Patent Document 1 discloses an ejector refrigeration cycle which is a vapor compression refrigeration cycle apparatus including an ejector as a refrigerant decompression device.

The ejector refrigeration cycle of this Patent Document 1 is applied to an air conditioner. Furthermore, the ejector refrigeration cycle of Patent Document 1 includes a cooling mode refrigerant circuit that cools air blown into the air-conditioning target space, a heating mode refrigerant circuit that heats air blown into the air-conditioning target space, and cooling and dehumidification The refrigerant circuit or the like in the weak dehumidifying and heating mode that reheats the heated air can be switched.

More specifically, in the ejector-type refrigeration cycle of Patent Document 1, the refrigerant flows through the indoor condenser, which is a heat exchanger for heating, the outdoor heat exchanger, and the outdoor evaporator, which is a heat exchanger for cooling, in the weak dehumidifying heating mode. Is switched to a refrigerant circuit connected in series. And the air is cooled and dehumidified by the indoor evaporator, and the dehumidified air is reheated by the indoor condenser.

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

In the weak dehumidifying heating mode, the refrigerant circuit that switches the refrigerant flowing out of the outdoor heat exchanger to the cooling side nozzle portion of the cooling side ejector is switched. And the refrigerant | coolant is supplied to an indoor evaporator by the suction effect | action of the injection refrigerant | coolant injected from a cooling side nozzle part. Further, the coefficient of performance (COP) of the cycle is improved by sucking the refrigerant whose pressure is increased in the cooling side diffuser into the compressor.

JP 2014-206362 A

However, according to the study by the inventors of the present disclosure, when the ejector refrigeration cycle of Patent Document 1 is actually operated, it may not be possible to raise the air to a desired temperature in the weak dehumidifying heating mode. It was. Then, when the cause was investigated, in the weak dehumidification heating mode of patent document 1, in order to increase the heating capability of the air in an indoor condenser, it turned out that it is a cause to reduce the refrigerant | coolant pressure in an outdoor heat exchanger. It was.

Specifically, when 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 exhibit a sufficient suction action. And it becomes impossible to supply a refrigerant | coolant to an indoor evaporator, and it becomes impossible to operate an ejector type refrigerating cycle appropriately. As a result, the air cannot be raised to a desired temperature.

In other words, in the weak dehumidifying heating mode of Patent Document 1, in order to properly operate the ejector refrigeration cycle, the refrigerant pressure in the outdoor heat exchanger must be maintained at a predetermined value or higher. For this reason, in the weak dehumidification heating mode of patent document 1, the temperature adjustment range of the air ventilated to air-conditioning object space is restrict | limited.

Further, in a general refrigeration cycle apparatus, refrigeration oil for lubricating the compressor is mixed in the refrigerant. For this reason, if the refrigerant cannot be supplied to the indoor evaporator, the refrigerating machine oil flowing into the indoor evaporator cannot be pushed out to the suction side of the compressor, and the refrigerating machine oil may stay in the indoor evaporator. is there.

If the refrigeration oil stays in the indoor evaporator in this way, the refrigeration oil supplied to the compressor is reduced, causing deterioration in the durability of the compressor. Furthermore, the heat exchange performance of the indoor evaporator is reduced, which causes a reduction in the cooling capacity exhibited by the indoor evaporator when switching to the cooling mode or the like.

In view of the above points, the present disclosure is applicable to an air conditioner that performs dehumidifying heating, and can expand the temperature adjustment range of air during dehumidifying heating while suppressing refrigerating machine oil from staying in the heat exchanger. It is an object to provide a simple ejector type refrigeration cycle.

The ejector refrigeration cycle according to the first aspect of the present disclosure is applied to an air conditioner, and includes a compressor, a heat exchanger for heating, a first pressure reducing device, an outdoor heat exchanger, a second pressure reducing device, a heat exchanger for cooling, A heating side ejector, a heating side gas-liquid separator, and a refrigerant circuit switching device are provided.

Compressor compresses refrigerant mixed with refrigeration oil until it becomes high pressure refrigerant, and discharges high pressure refrigerant. The heating heat exchanger heats the air blown into the air-conditioning target space using the high-pressure refrigerant as a heat source. The first decompression device is disposed downstream of the heating heat exchanger and decompresses the refrigerant. The outdoor heat exchanger causes the refrigerant that has flowed out of the first decompression device to exchange heat with the outside air. The second decompression device is disposed on the downstream side of the heating heat exchanger and decompresses the refrigerant. The cooling heat exchanger evaporates the refrigerant flowing out of the second decompression device and cools the air before passing through the heating heat exchanger.

The heating side ejector has a heating side nozzle part, a heating side refrigerant suction port, and a heating side pressure raising part. A heating side nozzle part is arrange | positioned in the downstream of the heat exchanger for a heating, decompresses a refrigerant | coolant, and injects it as a heating side injection refrigerant | coolant. The heating side refrigerant suction port sucks the refrigerant as the heating side suction refrigerant by the suction action of the heating side injection refrigerant. The heating side pressurizing unit pressurizes the mixed refrigerant of the heating side injection refrigerant and the heating side suction refrigerant. The heating-side gas-liquid separator separates the refrigerant that has flowed out of the heating-side pressure increasing unit into a gas-phase refrigerant and a liquid-phase refrigerant.

The refrigerant circuit switching device switches the refrigerant circuit. In the first dehumidifying and heating mode in which the air cooled by the cooling heat exchanger is reheated by the heating heat exchanger, the refrigerant circuit switching device converts the refrigerant flowing out of the heating heat exchanger to the first pressure reducing device. The refrigerant circuit is switched in the order of the outdoor heat exchanger, the second decompressor, the cooling heat exchanger, and the compressor. In the second dehumidifying and heating mode in which the air cooled by the rejection heat exchanger is reheated by the heating heat exchanger, the refrigerant circuit switching device converts the refrigerant flowing out of the heating heat exchanger to the second decompression device. The refrigerant circuit is switched in the order of the cooling heat exchanger, the first decompressor, the outdoor heat exchanger, and the compressor. In the heating mode in which air is heated by the heating heat exchanger, the refrigerant circuit switching device allows the refrigerant that has flowed out of the heating heat exchanger to flow into the heating-side nozzle portion and the gas that has flowed out of the heating-side gas-liquid separator. A refrigerant circuit that sucks phase refrigerant into the compressor, causes liquid phase refrigerant flowing out of the heating side gas-liquid separator to flow into the outdoor heat exchanger, and sucks refrigerant flowing out of the outdoor heat exchanger from the heating side refrigerant suction port Switch to.

The flow direction of the refrigerant in the outdoor heat exchanger in the first dehumidifying and heating mode is the same as the flow direction of the refrigerant in the outdoor heat exchanger in the second dehumidifying and heating mode. The refrigerant flow direction in the outdoor heat exchanger in the first dehumidifying heating mode is different from the refrigerant flow direction in the outdoor heat exchanger in the heating mode.

According to this, in the heating mode, the refrigerant circuit switching device switches to the refrigerant circuit that sucks the gas-phase refrigerant flowing out from the heating side gas-liquid separator into the compressor. Can be sucked into the compressor. Therefore, the power consumption of the compressor is reduced and the coefficient of performance (COP) of the cycle is improved as compared with a normal refrigeration cycle apparatus in which the refrigerant evaporation pressure in the outdoor heat exchanger and the suction refrigerant pressure of the compressor are equal. Can do.

In the first and second dehumidifying and heating modes, the refrigerant circuit switching device switches to a refrigerant circuit in which the outdoor heat exchanger and the cooling heat exchanger are connected in series with the refrigerant flow. Therefore, regardless of the refrigerant pressure in the outdoor heat exchanger, the refrigerant can be reliably supplied to the cooling heat exchanger by the suction and discharge action of the compressor.

According to the first aspect of the present disclosure, in the first dehumidifying and heating mode, the refrigerant circuit switching device converts the refrigerant that has flowed out of the heat exchanger for heating into the first decompression device, the outdoor heat exchanger, the second decompression device, and the cooling. Switch to the refrigerant circuit that flows in the order of the heat exchanger for compressor and the compressor. That is, the outdoor heat exchanger is disposed on the upstream side of the refrigerant flow with respect to the cooling heat exchanger via the second pressure reducing device. As a result, the refrigerant temperature in the outdoor heat exchanger can be set higher than the refrigerant temperature in the cooling heat exchanger. Accordingly, it is possible to adjust the refrigerant heat dissipation amount in the heating heat exchanger by adjusting the refrigerant heat absorption / release heat amount in the outdoor heat exchanger.

Further, in the second dehumidifying and heating mode, the refrigerant circuit switching device converts the refrigerant flowing out from the heating heat exchanger into the second decompression device, the cooling heat exchanger, the first decompression device, the outdoor heat exchanger, and the compressor. Switch to the refrigerant circuit to be circulated in order. That is, the outdoor heat exchanger is disposed downstream of the refrigerant flow with respect to the cooling heat exchanger via the first pressure reducing device. As a result, the refrigerant temperature in the outdoor heat exchanger can be set to a temperature range lower than the refrigerant temperature in the cooling heat exchanger. Therefore, the heat absorption amount of the refrigerant in the outdoor heat exchanger can be increased, and the air can be heated with a heating capability higher than that in the first dehumidifying and heating mode in the heating heat exchanger.

As a result, when dehumidifying and heating the air-conditioning target space, the temperature of the air can be adjusted in a wide temperature range by switching between the first dehumidifying and heating mode and the second dehumidifying and heating mode.

Moreover, since the flow direction of the refrigerant in the outdoor heat exchanger in the first and second dehumidifying and heating modes is different from the flow direction of the refrigerant in the outdoor heat exchanger in the heating mode, the outdoor in the first and second dehumidifying and heating modes The flow mode of the refrigerant in the heat exchanger and the flow mode of the refrigerant in the outdoor heat exchanger during the heating mode can be changed. Thereby, it can suppress that refrigerating machine oil retains in an outdoor heat exchanger.

That is, according to the first aspect of the present disclosure, in the ejector-type refrigeration cycle applied to the air conditioner that performs dehumidifying heating, the refrigerating machine oil is prevented from staying in the outdoor heat exchanger, and the air during dehumidifying heating is suppressed. The temperature adjustment range can be expanded.

The ejector refrigeration cycle according to the second aspect of the present disclosure is applied to an air conditioner, and includes a compressor, a heat exchanger for heating, a first pressure reducing device, an outdoor heat exchanger, a second pressure reducing device, a cooling heat exchanger, A cooling side ejector, a cooling side gas-liquid separator, and a refrigerant circuit switching device may be provided. The configurations of the compressor, the heat exchanger for heating, the first pressure reducing device, the outdoor heat exchanger, the second pressure reducing device, and the cooling heat exchanger are the same as those of the first aspect described above.

The cooling side ejector has a cooling side nozzle portion, a cooling side refrigerant suction port, and a cooling side pressure increasing portion. A cooling side nozzle part is arrange | positioned in the downstream of the heat exchanger for a heating, decompresses a refrigerant | coolant, and injects it as a cooling side injection refrigerant | coolant. The cooling side refrigerant suction port sucks the refrigerant as the cooling side suction refrigerant by the suction action of the cooling side injection refrigerant. The cooling side boosting unit boosts the mixed refrigerant of the cooling side injection refrigerant and the cooling side suction refrigerant. The cooling-side gas-liquid separator separates the refrigerant that has flowed out of the cooling-side booster into a gas-phase refrigerant and a liquid-phase refrigerant.

The refrigerant circuit switching device switches the refrigerant circuit. Specifically, the refrigerant circuit switching device switches the refrigerant circuit in the first dehumidifying and heating mode and the second dehumidifying and heating mode, similarly to the first aspect described above. However, according to the second aspect, in the cooling mode in which the air is cooled by the cooling heat exchanger, the refrigerant circuit switching device causes the refrigerant that has flowed out of the outdoor heat exchanger to flow into the cooling side nozzle portion, The gas-phase refrigerant that has flowed out of the gas-liquid separator is sucked into the compressor, and the liquid-phase refrigerant that has flowed out of the cooling-side gas-liquid separator is flowed into the cooling heat exchanger, and the refrigerant that has flowed out of the cooling heat exchanger is removed. Switch to the refrigerant circuit to be sucked from the cooling side refrigerant suction port.

The refrigerant flow direction in the cooling heat exchanger in the first dehumidifying heating mode is the same as the refrigerant flow direction in the cooling heat exchanger in the second dehumidifying heating mode. The refrigerant flow direction in the cooling heat exchanger in the first dehumidifying heating mode is different from the refrigerant flow direction in the cooling heat exchanger in the cooling mode.

According to this, in the cooling mode, the refrigerant circuit switching device switches to the refrigerant circuit that sucks the gas-phase refrigerant flowing out from the cooling side gas-liquid separator into the compressor. Can be sucked into the compressor. Therefore, the power consumption of the compressor is reduced and the coefficient of performance (COP) of the cycle is improved as compared with a normal refrigeration cycle apparatus in which the refrigerant evaporation pressure in the heat exchanger for cooling is equal to the suction refrigerant pressure of the compressor. be able to.

In the first and second dehumidifying and heating modes, the refrigerant circuit switching device is switched to a refrigerant circuit in which the outdoor heat exchanger and the cooling heat exchanger are connected in series with the refrigerant flow. Therefore, similarly to the first aspect described above, the refrigerant can be reliably supplied to the cooling heat exchanger by the suction and discharge action of the compressor regardless of the refrigerant pressure in the outdoor heat exchanger.

The refrigerant circuit switching device of the second aspect switches the refrigerant circuit in the first dehumidifying and heating mode and the second dehumidifying and heating mode in the same manner as in the first aspect. Therefore, according to the second aspect, the temperature of the blown air can be adjusted in a wide temperature range as in the first aspect.

Further, the flow direction of the refrigerant in the cooling heat exchanger in the first and second dehumidifying heating modes is different from the flow direction of the refrigerant in the cooling heat exchanger in the heating mode. Therefore, the flow mode of the refrigerant in the cooling heat exchanger in the first and second dehumidifying heating modes and the flow mode of the refrigerant in the cooling heat exchanger in the heating mode can be changed. Similarly, it is possible to suppress the refrigeration oil from staying in the cooling heat exchanger.

That is, according to the second aspect of the present disclosure, in the ejector-type refrigeration cycle applied to an air conditioner that performs dehumidifying heating, the air during dehumidifying heating is suppressed while the refrigerating machine oil is prevented from staying in the cooling heat exchanger. The temperature adjustment range can be expanded.

The above and other objects, features and advantages of the present disclosure will become more apparent from the following detailed description with reference to the accompanying drawings.
1 is an overall configuration diagram of a vehicle air conditioner. It is a whole block diagram which shows the refrigerant circuit at the time of the air_conditioning | cooling mode of an ejector-type refrigerating cycle. It is a whole block diagram which shows the refrigerant circuit at the time of the 1st dehumidification heating mode of an ejector type refrigeration cycle. It is a whole block diagram which shows the refrigerant circuit at the time of the 2nd dehumidification heating mode of an ejector type refrigeration cycle. It is a whole lineblock diagram showing the refrigerant circuit at the time of heating mode of an ejector type refrigerating cycle. It is a whole lineblock diagram showing the refrigerant circuit at the time of defrosting mode of an ejector type freezing cycle. It is a block diagram which shows the electric control part of the vehicle air conditioner. It is a Mollier diagram which shows the state of the refrigerant | coolant at the time of the air_conditioning | cooling mode of an ejector-type refrigerating cycle. It is a Mollier diagram which shows the state of the refrigerant | coolant at the time of the 1st dehumidification heating mode of an ejector type refrigeration cycle. It is a Mollier diagram which shows the state of the refrigerant | coolant at the time of the 2nd dehumidification heating mode of an ejector-type refrigerating cycle. It is a Mollier diagram which shows the state of the refrigerant | coolant at the time of the heating mode of an ejector type refrigeration cycle. It is a Mollier diagram which shows the state of the refrigerant | coolant at the time of the defrost mode of an ejector-type refrigerating cycle. It is explanatory drawing for demonstrating the temperature adjustable range of the air of an ejector-type refrigerating cycle.

An embodiment of the present disclosure will be described with reference to FIGS. In the present embodiment, an ejector refrigeration cycle 10 according to the present disclosure is applied to a vehicle air conditioner 1 mounted on an electric vehicle as shown in the overall configuration diagram of FIG. The ejector-type refrigeration cycle 10 functions to heat or cool air (air blown 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 air blown into the vehicle interior.

Further, as shown in FIGS. 2 to 6, the ejector-type refrigeration cycle 10 includes a cooling mode refrigerant circuit (see FIG. 2), a first dehumidifying and heating mode refrigerant circuit (see FIG. 3), and a second dehumidifying and heating mode. The refrigerant circuit (see FIG. 4), the heating mode refrigerant circuit (see FIG. 5), and the defrost mode refrigerant circuit (see FIG. 6) can be switched.

The cooling mode is an operation mode in which air is cooled to cool the passenger compartment. The first dehumidifying and heating mode is an operation mode in which the air that has been cooled and dehumidified is reheated to perform dehumidifying heating in the passenger compartment. The second dehumidifying and heating mode is an operation mode in which the air is reheated with a heating capability higher than that in the first dehumidifying and heating mode to perform dehumidifying heating in the passenger compartment. The heating mode is an operation mode in which air is heated to heat the vehicle interior. The defrosting mode is an operation mode for removing frost formation in the outdoor heat exchanger 17 described later.

2 to 6, the arrangement of the components of the ejector refrigeration cycle 10 shown in FIG. 1 is changed in order to clarify the flow direction of the refrigerant in each operation mode. Specifically, the heating side ejector 16, the outdoor heat exchanger 17 and the like, and the cooling side ejector 22, the indoor evaporator 21 and the like are arranged symmetrically.

Accordingly, the ejector refrigeration cycle 10 shown in FIG. 1 is equivalent to the ejector refrigeration cycle 10 shown in FIGS. Moreover, in FIGS. 2-6, the flow of the refrigerant | coolant in each operation mode is shown by the solid line arrow.

Further, the ejector refrigeration cycle 10 employs an HFC refrigerant (specifically, R134a) as the refrigerant, and constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the refrigerant critical pressure. . Furthermore, refrigeration oil for lubricating the compressor 11 is mixed in the refrigerant. As this refrigerating machine oil, PAG oil (polyalkylene glycol oil) having compatibility with the liquid phase refrigerant is employed. A part of the refrigerating machine oil circulates in the cycle together with the refrigerant.

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

The refrigerant inlet side of the indoor condenser 12 is connected to the discharge port of the compressor 11. The indoor condenser 12 is arrange | positioned in the casing 31 which forms the air path of air in the indoor air conditioning unit 30 mentioned later. The indoor condenser 12 is a heating heat exchanger that heats air using the high-pressure refrigerant as a heat source by causing heat exchange between the high-pressure refrigerant discharged from the compressor 11 and air after passing through an indoor evaporator 21 described later. Details of the indoor air conditioning unit 30 will be described later.

The refrigerant outlet of the indoor condenser 12 is connected to one inlet / outlet side of the first four-way valve 13a. The first four-way valve 13a is a refrigerant circuit switching device that switches the refrigerant circuit of the ejector refrigeration cycle 10 together with a second four-way valve 13b, which will be described later.

The first four-way valve 13a connects the refrigerant outlet side of the indoor condenser 12 and one inlet / outlet side of the first three-way joint 14a, and at the same time, one inlet / outlet side of the second four-way valve 13b and one of the third three-way joint 14c. It is possible to switch to a refrigerant circuit that connects the inlet / outlet side. Specifically, the one inlet / outlet side of the first three-way joint 14a is an inlet / outlet side of a heating side ejector 16 or an outdoor heat exchanger 17 described later. Specifically, the one inlet / outlet side of the third three-way joint 14c is an outlet / inlet side of the cooling side ejector 22 or the indoor evaporator 21 described later.

Further, the first four-way valve 13a connects the refrigerant outlet side of the indoor condenser 12 and one inlet / outlet side of the third three-way joint 14c, and at the same time, connects one inlet / outlet side of the second four-way valve 13b and the first three-way joint 14a. It can switch to the refrigerant circuit which connects one entrance / exit side. The operations of the first four-way valve 13 a and the second four-way valve 13 b are controlled by a control voltage output from the air conditioning control device 40.

The first three-way joint 14a is a pipe joint having three refrigerant outlets. Further, the ejector refrigeration cycle 10 includes second to fourth three-way joints 14b to 14d, as will be described later. The basic configuration of the second to fourth three-way joints 14b to 14d is the same as that of the first three-way joint 14a.

The other inlet / outlet of the first three-way joint 14a is connected to the inlet side of the heating side nozzle portion 16a of the heating side ejector 16 via the first flow rate adjusting valve 15a. One inlet / outlet side of the second three-way joint 14b is connected to another inlet / outlet of the first three-way joint 14a via a second flow rate adjusting valve 15b.

The first flow rate adjusting valve 15a is an electric type that includes 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 a variable aperture mechanism. The first flow rate adjusting valve 15a adjusts the flow rate of the refrigerant flowing into the heating side nozzle portion 16a of the heating side ejector 16 at least in the heating mode. The second flow rate adjustment valve 15 b is a first decompression device that decompresses the refrigerant that flows downstream of the indoor condenser 12 and flows into the outdoor heat exchanger 17.

Furthermore, the ejector refrigeration cycle 10 includes second to sixth flow rate adjusting valves 15b to 15f. The basic configuration of the second to sixth flow rate adjustment valves 15b to 15f is the same as that of the first flow rate adjustment valve 15a. The first to sixth flow rate adjusting valves 15a to 15f are fully opened functions that function as simple refrigerant passages without fully exhibiting the flow rate adjusting action and the refrigerant pressure reducing action by fully opening the valve opening degree, and the valve opening degree is fully increased. It has a fully closed function of closing the refrigerant flow path by closing.

The first to sixth flow rate adjustment valves 15a to 15f can switch the refrigerant circuit in each operation mode by the fully open function and the fully closed function. Accordingly, the first to sixth flow rate adjusting valves 15a to 15f have a function as a refrigerant circuit switching device together with the first four-way valve 13a and the second four-way valve 13b. The operations of the first to sixth flow rate adjusting valves 15 a to 15 f are controlled by a control signal (control pulse) output from the air conditioning control device 40.

One refrigerant inlet / outlet side of the outdoor heat exchanger 17 is connected to another inlet / outlet of the second three-way joint 14b. The heating side refrigerant suction port 16c side of the heating side ejector 16 is connected to the other opening / closing port of the second three-way joint 14b via the first on-off valve 18a.

The first on-off valve 18a is an electromagnetic valve that opens and closes a refrigerant passage that connects the second three-way joint 14b and the heating-side refrigerant suction port 16c of the heating-side ejector 16. Further, the ejector refrigeration cycle 10 includes a second on-off valve 18b as will be described later. The basic configuration of the second on-off valve 18b is the same as that of the first on-off valve 18a.

Further, the first on-off valve 18a and the second on-off valve 18b can switch the refrigerant circuit in each operation mode described above by opening and closing the refrigerant passage. Therefore, the 1st on-off valve 18a and the 2nd on-off valve 18b comprise a refrigerant circuit switching apparatus with the 1st four-way valve 13a and the 2nd four-way valve 13b. The operations of the first on-off valve 18 a and the second on-off valve 18 b are controlled by a control voltage output from the air conditioning control device 40.

The outdoor heat exchanger 17 is a heat exchanger that is disposed in the vehicle bonnet and exchanges heat between the refrigerant flowing through the vehicle hood and the outside air blown from a blower fan (not shown). The outdoor heat exchanger 17 functions as a radiator that radiates high-pressure refrigerant at least in the cooling mode. Further, at least in the second dehumidifying heating mode and the heating mode, it functions as an evaporator that evaporates the refrigerant.

The liquid refrigerant inlet / outlet side of the heating side accumulator 19 is connected to the other refrigerant inlet / outlet of the outdoor heat exchanger 17 via a third flow rate adjusting valve 15c.

In the present embodiment, the outdoor heat exchanger 17 employs a refrigerant whose cross-sectional area of the refrigerant passage formed therein changes in the refrigerant flow direction. More specifically, the outdoor heat exchanger 17 of the present embodiment is a so-called tank and tube type heat exchanger. And 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 heat exchanger is a group of tubes that flow the refrigerant in the same distribution space formed in the tank in the same direction toward the same collective space formed in the tank. It can be defined as a refrigerant passage formed by Therefore, the passage sectional area of the path (refrigerant passage) (total passage sectional area of the tube) can be changed by changing the number of tubes constituting the path.

The outdoor heat exchanger 17 of the present embodiment has a path configuration in which the passage cross-sectional area of the refrigerant passage formed therein gradually decreases as it goes from the other refrigerant inlet / outlet side to the one refrigerant inlet / outlet side. Yes. The other refrigerant inlet / outlet in the present embodiment is an inlet / outlet on the side to which the liquid-phase refrigerant inlet / outlet of the heating side accumulator 19 is connected, and the other refrigerant inlet / outlet is connected to another inlet / outlet of the second three-way joint 14b. This is the side entrance.

Next, the heating-side ejector 16 functions as a decompression device that decompresses the refrigerant flowing out of the indoor condenser 12 at least in the heating mode. Furthermore, the heating-side ejector 16 functions as a refrigerant transport device that sucks and transports the refrigerant that has flowed out of the outdoor heat exchanger 17 by the suction action of the jetted refrigerant that is injected at a high speed.

More specifically, the heating side ejector 16 has a heating side nozzle portion 16a and a heating side body portion 16b. The heating-side nozzle portion 16a is formed of a substantially cylindrical member made of metal (in this embodiment, made of stainless steel) that gradually tapers in the refrigerant flow direction. And a refrigerant | coolant is decompressed isentropically in the refrigerant path formed in the inside.

In the refrigerant passage formed inside the heating side nozzle portion 16a, a throat portion (minimum passage area portion) having the smallest passage cross-sectional area is formed, and further toward the refrigerant injection port for injecting refrigerant from the throat portion. Accordingly, a divergent portion in which the refrigerant passage area is enlarged is formed. That is, the heating side nozzle part 16a is configured as a Laval nozzle.

Further, in the present embodiment, as the heating-side nozzle portion 16a, one that is set so that the flow rate of the heating-side injection refrigerant that is injected from the refrigerant injection port becomes equal to or higher than the sonic speed during normal operation of the ejector refrigeration cycle 10 is adopted. Has been. Of course, you may comprise the heating side nozzle part 16a with a tapered nozzle.

The heating side body portion 16b is formed of a cylindrical member made of metal (in this embodiment, made of an aluminum alloy), functions as a fixing member that supports and fixes the heating side nozzle portion 16a therein, and is also used as a heating side ejector. 16 outer shells are formed. More specifically, the heating-side nozzle portion 16a is fixed by press-fitting so as to be housed inside one end side in the longitudinal direction of the heating-side body portion 16b. Therefore, the refrigerant does not leak from the fixing portion (press-fit portion) between the heating side nozzle portion 16a and the heating side body portion 16b.

Further, in the outer peripheral surface of the heating side body portion 16b, a portion corresponding to the outer peripheral side of the heating side nozzle portion 16a is provided so as to penetrate the inside and outside and communicate with the refrigerant injection port of the heating side nozzle portion 16a. A heating-side refrigerant suction port 16c is formed. The heating-side refrigerant suction port 16c is a through hole that sucks the refrigerant that has flowed out of the outdoor heat exchanger 17 into the heating-side ejector 16 by the suction action of the heating-side injection refrigerant that is injected from the heating-side nozzle portion 16a. .

Further, inside the heating side body portion 16b, a suction passage that guides the suction refrigerant sucked from the heating side refrigerant suction port 16c to the refrigerant injection port side of the heating side nozzle portion 16a, and the heating side ejector 16 through the suction passage. A heating side diffuser portion 16d, which is a heating side pressure increasing portion that increases the pressure by mixing the heating side suction refrigerant and the heating side injection refrigerant that have flowed into the inside, is formed.

The heating-side diffuser portion 16d is disposed so as to be continuous with the outlet of the suction passage, and is formed so that the refrigerant passage area gradually increases. Thereby, while mixing the heating side injection refrigerant and the heating side suction refrigerant, the function of decelerating the flow rate and increasing the pressure of the mixed refrigerant of the heating side injection refrigerant and the heating side suction refrigerant, that is, the speed of the mixed refrigerant It functions to convert energy into pressure energy.

The inlet side of the heating side accumulator 19 is connected to the refrigerant outlet of the heating side diffuser portion 16d. The heating-side accumulator 19 is a heating-side gas-liquid separator that separates the refrigerant flowing out from the heating-side diffuser portion 16d of the heating-side ejector 16 into a gas-phase refrigerant and a liquid-phase refrigerant. The heating-side accumulator 19 is provided with a gas phase refrigerant inlet / outlet for allowing the separated gas phase refrigerant to flow out and a liquid phase refrigerant inlet / outlet for allowing the separated liquid phase refrigerant to flow out.

In the present embodiment, a heating-side accumulator 19 having a relatively small internal volume is employed. For this reason, the heating-side accumulator 19 allows the separated liquid-phase refrigerant to flow out from the liquid-phase refrigerant inlet / outlet with little storage. Moreover, the refrigerant | coolant which cannot be made to flow out of a liquid phase refrigerant | coolant inlet / outlet among the isolate | separated liquid phase refrigerant | coolants may flow out of a gaseous-phase refrigerant | coolant outflow port.

The gas phase refrigerant inlet / outlet of the heating side accumulator 19 is connected to another inlet / outlet side of the second four-way valve 13b which is a refrigerant circuit switching device.

The second four-way valve 13b connects the gas-phase refrigerant inlet / outlet side of the heating-side accumulator 19 and one inlet / outlet side of the first four-way valve 13a, and at the same time, the gas-phase refrigerant inlet / outlet side of the cooling-side accumulator 23 and the suction-side accumulator 24. It is possible to switch to a refrigerant circuit connecting the inlet side.

Further, the second four-way valve 13b connects the gas-phase refrigerant inlet / outlet side of the heating-side accumulator 19 and the inlet side of the suction-side accumulator 24, and at the same time, the gas-phase refrigerant inlet / outlet of the cooling-side accumulator 23 and one of the first four-way valves 13a. It can switch to the refrigerant circuit which connects an entrance / exit side.

Further, the inlet side of the cooling side nozzle portion 22a of the cooling side ejector 22 is connected to another outlet / inlet of the third three-way joint 14c to which the first four-way valve 13a is connected via the fourth flow rate adjusting valve 15d. . One further inlet / outlet side of the fourth three-way joint 14d is connected to another inlet / outlet of the third three-way joint 14c via a fifth flow rate adjusting valve 15e. The fifth flow rate adjustment valve 15 e is a second decompression device that decompresses the refrigerant that is downstream of the indoor condenser 12 and flows into the indoor evaporator 21.

One refrigerant inlet / outlet side of the indoor evaporator 21 is connected to another inlet / outlet of the fourth three-way joint 14d. The heating side gas-liquid separator 22c side of the cooling side ejector 22 is connected to another inlet / outlet of the fourth three-way joint 14d via the second on-off valve 18b.

The indoor evaporator 21 is disposed in the casing 31 of the indoor air conditioning unit 30 and on the upstream side of the air flow from the indoor condenser 12 described above. The indoor evaporator 21 heats the low-pressure refrigerant decompressed by the fifth flow rate adjustment valve 15e or the sixth flow rate adjustment valve 15f by exchanging heat with air to evaporate it, thereby cooling the air by exerting an endothermic effect. It is an exchanger.

The liquid refrigerant inlet / outlet side of the cooling side accumulator 23 is connected to the other refrigerant inlet / outlet of the indoor evaporator 21 via a sixth flow rate adjusting valve 15f.

In the present embodiment, the indoor evaporator 21 is a so-called tank-and-tube heat exchanger similar to the outdoor heat exchanger 17, and the cross-sectional area of the refrigerant passage formed inside is the refrigerant flow direction. The one that changes toward is adopted.

More specifically, in the indoor evaporator 21 of the present embodiment, the passage cross-sectional area of the refrigerant passage formed inside decreases stepwise from the other refrigerant inlet / outlet side toward the one refrigerant inlet / outlet side. It has a path configuration. The other refrigerant inlet / outlet in the present embodiment is an inlet / outlet on the side to which the liquid-phase refrigerant inlet / outlet of the cooling side accumulator 23 is connected, and the other refrigerant inlet / outlet is connected to another inlet / outlet of the fourth three-way joint 14d. This is the side entrance.

The basic configuration of the cooling side ejector 22 is the same as that of the heating side ejector 16. Therefore, the cooling side ejector 22 has the cooling side nozzle part 22a and the cooling side body 22b. The cooling side body 22b is formed with a cooling side refrigerant suction port 22c and a cooling side diffuser portion 22d which is a cooling side boosting portion.

The inlet side of the cooling side accumulator 23 is connected to the refrigerant outlet of the cooling side diffuser part 22d. The cooling side accumulator 23 is a cooling side gas-liquid separator that separates the refrigerant flowing out from the cooling side diffuser portion 22d of the cooling side ejector 22 into a gas phase refrigerant and a liquid phase refrigerant. The cooling side accumulator 23 is provided with a gas phase refrigerant outlet for flowing out the separated gas phase refrigerant and a liquid phase refrigerant outlet for letting out the separated liquid phase refrigerant.

In the present embodiment, as the cooling side accumulator 23, a cooling side accumulator 23 having a relatively small internal volume is employed. For this reason, the cooling-side accumulator 23 causes the separated liquid-phase refrigerant to flow out from the liquid-phase refrigerant inlet / outlet with little storage. Moreover, the refrigerant | coolant which cannot be made to flow out of a liquid phase refrigerant | coolant inlet / outlet among the isolate | separated liquid phase refrigerant | coolants may flow out of a gaseous-phase refrigerant | coolant outflow port.

The gas phase refrigerant inlet / outlet port of the cooling side accumulator 23 is connected to another inlet / outlet side of the second four-way valve 13b which is a refrigerant circuit switching device. The suction side accumulator 24 is a gas-liquid separator that separates the refrigerant sucked into the compressor 11 into a gas phase refrigerant and a liquid phase refrigerant. The suction-side accumulator 24 allows the separated gas-phase refrigerant to flow out to the suction port side of the compressor 11 and stores excess refrigerant in the cycle.

Next, the indoor air conditioning unit 30 will be described. The indoor air conditioning unit 30 is for blowing out the air whose temperature has been adjusted by the ejector refrigeration cycle 10 into the vehicle interior, and is disposed inside (in the vehicle interior) of the instrument panel (instrument panel) at the foremost interior of the vehicle interior. . The indoor air conditioning unit 30 is configured by housing a blower 32, an indoor evaporator 21, an indoor condenser 12, an air mix door 34, and the like in a casing 31 that forms an outer shell thereof.

The casing 31 forms an air passage for air blown into the passenger compartment, and is formed of a resin (for example, polypropylene) having a certain degree of elasticity and excellent strength. On the most upstream side of the air flow in the casing 31, an inside / outside air switching device 33 is disposed as an inside / outside air switching unit for switching and introducing inside air (vehicle compartment air) and outside air (vehicle compartment outside air) into the casing 31. Yes.

The inside / outside air switching device 33 continuously adjusts the opening area of the inside air introduction port through which the inside air is introduced into the casing 31 and the outside air introduction port through which the outside air is introduced by the inside / outside air switching door, so that the air volume of the inside air and the air volume of the outside air are adjusted. The air volume ratio 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 32 as a blower that blows air sucked through the inside / outside air switching device 33 toward the vehicle interior is disposed on the downstream side of the air flow of the inside / outside air switching device 33. The blower 32 is an electric blower that drives a centrifugal multiblade fan (sirocco fan) with an electric motor, and the number of rotations (air flow rate) is controlled by a control voltage output from the air conditioning control device 40.

The indoor evaporator 21 and the indoor condenser 12 are arranged in this order on the downstream side of the air flow of the blower 32. That is, the indoor evaporator 21 is disposed upstream of the indoor condenser 12 in the air flow. Further, on the downstream side of the air flow of the indoor evaporator 21 and the upstream side of the air flow of the indoor condenser 12, the ratio of the amount of air passing through the indoor condenser 12 in the air after passing through the indoor evaporator 21 is set. An air mix door 34 to be adjusted is disposed.

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

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

These face opening hole, foot opening hole, and defroster opening hole are respectively connected to a face air outlet, a foot air outlet, and a defroster air outlet (not shown) through a duct that forms an air passage. )It is connected to the.

Therefore, the air mix door 34 adjusts the air volume ratio between the air volume that passes through the indoor condenser 12 and the air volume that bypasses the indoor condenser 12, thereby adjusting the temperature of the conditioned air mixed in the mixing space. . Thereby, the temperature of the air (air conditioned air) blown out from each outlet to the vehicle interior is adjusted.

That is, the air mix door 34 functions as a temperature adjusting 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 control device 40.

In addition, on the upstream side of the air flow of the face opening hole, foot opening hole, and defroster opening hole, a face door that adjusts the opening area of the face opening hole, a foot door that adjusts the opening area of the foot opening hole, and a defroster opening hole, respectively A defroster door (none of which is shown) for adjusting the opening area 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 an outlet mode door via a link mechanism or the like. 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 a blowout mode in which the face blowout is fully opened and air is blown out from the face blowout toward the upper body of the passenger in the passenger compartment. The bi-level mode is an air outlet mode in which both the face air outlet and the foot air outlet are opened and air is blown toward the upper body and the feet of the passengers in the passenger compartment. The foot mode is a blow-out mode in which the foot blow-out opening is fully opened and the defroster blow-out opening is opened by a small opening so that air is mainly blown out from the foot blow-out opening.

Furthermore, when the occupant manually operates a blow mode switching switch provided on the operation panel 50, the defroster mode in which the defroster blowout port is fully opened and air is blown out from the defroster blowout port to the inner surface of the front windshield of the vehicle can be set.

Next, the electric control unit (ECU) of this embodiment will be described. The air conditioning control device 40 includes a known microcomputer including a CPU, a ROM, a RAM, and the like and peripheral circuits thereof. The air conditioning control device 40 performs various calculations and processes based on the control program stored in the ROM, and controls the operation of various control target devices connected to the output side. The various devices to be controlled are, for example, the compressor 11, the first four-way valve 13a, the second four-way valve 13b, the flow rate adjusting valves 15a-15f, the first on-off valve 18a, the second on-off valve 18b, the blower 32, and the like.

Further, on the input side of the air conditioning control device 40, as shown in the block diagram of FIG. 7, 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 indoor temperature sensor, An evaporator temperature sensor 46, an air-conditioning air temperature sensor 47, and the like are connected. And the detection signal of these sensor groups is input into the air-conditioning control apparatus 40. FIG.

The inside air temperature sensor 41 is an inside air temperature detecting unit that detects a vehicle interior temperature (inside air temperature) Tr. The outside air temperature sensor 42 is an outside air temperature detecting unit that detects a vehicle compartment outside temperature (outside air temperature) Tam. The solar radiation sensor 43 is a solar radiation amount detection unit that detects the solar radiation amount As irradiated into the vehicle interior. The outdoor heat exchanger temperature sensor 44 is an outdoor heat exchanger temperature detection unit that detects a refrigerant temperature (outdoor heat exchanger temperature) Tout in the outdoor heat exchanger. The discharge temperature sensor 45 is a discharge temperature detection unit that detects the discharge refrigerant temperature Td of the compressor 11. The indoor evaporator temperature sensor 46 is an evaporator temperature detector that detects a refrigerant evaporation temperature (indoor evaporator temperature) Tefin in the indoor evaporator 21. The conditioned air temperature sensor 47 is an conditioned air temperature detector that detects an air temperature TAV that is blown from the mixed space into the vehicle interior.

Further, as shown in FIG. 7, an operation panel 50 disposed near the instrument panel in the front part of the vehicle interior is connected to the input side of the air conditioning control device 40, and various operation switches provided on the operation panel 50 are connected. The operation signal is input. As various operation switches provided on the operation panel 50, there are 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 that sets or cancels the automatic control operation of the vehicle air conditioner 1. The cooling switch (A / C switch) is an input unit that requests cooling of 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.

In addition, the air-conditioning control device 40 of this embodiment is configured such that a control unit that controls various devices to be controlled connected to the output side is integrally configured. A configuration (hardware and software) that controls the operation of each of the various control target devices constitutes a control unit that controls the operation of each of the various control target devices.

For example, in the air-conditioning control device 40, the configuration for controlling the refrigerant discharge capability (rotation speed) of the compressor 11 constitutes a discharge capability control unit. Moreover, the structure which controls the action | operation of refrigerant circuit switching apparatuses, such as the 1st on-off valve 18a and the 2nd on-off valve 18b, comprises the refrigerant circuit control part.

Next, the operation of this embodiment in the above configuration will be described. As described above, in the ejector type refrigeration cycle 10 of the present embodiment, the operation of the cooling mode, the first dehumidifying heating mode, the second dehumidifying heating mode, the heating mode, and the defrosting mode can be switched.

These operation modes are switched by executing an air conditioning control program stored in advance in the 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, the detection signals of the above-mentioned air conditioning control sensor groups and the operation signals from various air conditioning operation switches are read. And based on the value of the read detection signal and operation signal, the target blowing temperature TAO which is the target temperature of the blowing air which blows off into the vehicle interior is calculated based on the following formula F1.

TAO = Kset × Tset−Kr × Tr−Kam × Tam−Ks × As + C (F1)
Note that Tset is the vehicle interior set temperature set by the temperature setting switch, Tr is the vehicle interior temperature (inside air temperature) detected by the inside air sensor, Tam is the outside air temperature detected by the outside air sensor, and As is detected by the solar radiation sensor. The amount of solar radiation. Kset, Kr, Kam, 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.

In the state where the cooling switch is turned on, when the target outlet temperature TAO is equal to or higher than the cooling reference temperature α and the outside air temperature Tam is higher than the predetermined dehumidifying heating reference temperature β, Operation in the first dehumidifying and heating mode is executed. Further, in the state where the cooling switch is turned on, when the target blowing 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, the second dehumidifying heating is performed. Run in mode.

Also, when the cooling switch is not turned on, the operation in the heating mode is executed. Further, when frost formation occurs in the outdoor heat exchanger 17 during the execution of the heating mode or the like, a defrosting operation is performed to remove the frost formation.

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. The operation in the first and second dehumidifying heating modes is executed mainly in early spring or early winter. In addition, when the outside air temperature is relatively low, such as in winter, the operation in the heating mode is executed. The operation in each operation mode will be described below.

(A) Cooling mode In the cooling mode, the air conditioning control device 40 connects the refrigerant outlet side of the indoor condenser 12 and the first three-way joint 14a side, and simultaneously connects the second four-way valve 13b side and the third three-way joint 14c side. The operation of the first four-way valve 13a is controlled so as to switch to the refrigerant circuit to be connected. Further, the refrigerant circuit connecting the gas-phase refrigerant inlet / outlet side of the heating-side accumulator 19 and the first four-way valve 13a side is simultaneously switched to the refrigerant circuit connecting the gas-phase refrigerant inlet / outlet side of the cooling-side accumulator 23 and the inlet side of the suction-side accumulator 24. Thus, the operation of the second four-way valve 13b is controlled.

In addition, the air conditioning controller 40 sets the first flow rate adjustment valve 15a to a fully closed state, sets the second flow rate adjustment valve 15b to a fully open state, sets the third flow rate adjustment valve 15c to a fully open state, and sets the fourth flow rate adjustment valve 15d to the refrigerant. The throttle state in which the pressure reducing action is exerted is set, the fifth flow rate adjustment valve 15e is fully closed, and the sixth flow rate adjustment valve 15f is set in the throttle state. Further, the air conditioning control device 40 closes the first on-off valve 18a and opens the second on-off valve 18b.

Thereby, in the cooling mode, as shown by the solid line arrow in FIG. 2, the compressor 11, the indoor condenser 12, the (second flow rate adjustment valve 15b), the outdoor heat exchanger 17, and the (third flow rate adjustment valve 15c). The refrigerant circulates in the order of the heating side accumulator 19, the fourth flow rate adjustment valve 15d, the cooling side ejector 22, the cooling side accumulator 23, the suction side accumulator 24, and the compressor 11, the cooling side accumulator 23, the sixth flow rate adjustment valve 15f, An ejector type refrigeration cycle in which the refrigerant circulates in the order of the indoor evaporator 21 and the cooling side refrigerant suction port 22c of the cooling side ejector 22 is configured.

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

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 evaporator outlet temperature TEO of the indoor evaporator 21 is determined based on the target outlet temperature TAO with reference to a control map stored in the air conditioning controller 40 in advance. This 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 in the indoor evaporator 21.

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 converted into 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

Further, the throttle opening degree of the fourth flow rate adjusting valve 15d, that is, the control signal (control pulse) output to the fourth flow rate adjusting valve 15d is stored in advance in the air conditioning control device 40 based on the target blowing temperature TAO. Determined with reference to the control map. Specifically, the COP of the ejector refrigeration cycle 10 is determined so as to approach the maximum value.

Further, the throttle opening degree of the sixth flow rate adjustment valve 15f, that is, the control signal (control pulse) output to the sixth flow rate adjustment valve 15f is determined as the reference opening degree for cooling stored in the air conditioning control device 40 in advance. Is done.

For 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 air after passing through the indoor evaporator 21 is It is determined to flow around the condenser 12.

Then, the control signals determined as described above are output to various control target devices. Thereafter, until the operation of the vehicle air conditioner 1 is requested to be stopped, the above-described detection signal and operation signal are read, the target blowing temperature TAO is calculated, the operating states of various control target devices are determined, and the control is performed every predetermined control cycle. Control routines such as voltage and control signal output are repeated. Such a control routine is repeated in the other operation modes.

Therefore, 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 a8 in FIG. 8) 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 air.

The refrigerant flowing out of the indoor condenser 12 flows into one refrigerant inlet / outlet of the outdoor heat exchanger 17 through the first four-way valve 13a, the fully opened second flow rate adjusting valve 15b, and the like. The refrigerant that has flowed into the outdoor heat exchanger 17 dissipates heat to the outside air blown from the blower fan in the outdoor heat exchanger 17 and condenses (point a8 to point e8 in FIG. 8).

The refrigerant that flows out from the other refrigerant inlet / outlet of the outdoor heat exchanger 17 flows into the heating-side accumulator 19 through the third flow rate adjusting valve 15c that is fully open, and is separated into a gas-phase refrigerant and a liquid-phase refrigerant. The The liquid-phase refrigerant separated by the heating-side accumulator 19 flows into the fourth flow rate adjustment valve 15d via the second four-way valve 13b, the first four-way valve 13a, etc., and is depressurized (from point e8 in FIG. 8). h8 points).

The refrigerant decompressed by the fourth flow rate adjustment valve 15d flows into the cooling side nozzle portion 22a of the cooling side ejector 22. The refrigerant that has flowed into the cooling-side nozzle portion 22a is isentropically decompressed and injected (from point h8 to point i8 in FIG. 8). And the refrigerant | coolant which flowed out from one refrigerant inlet / outlet of the indoor evaporator 21 is attracted | sucked from the cooling side refrigerant | coolant suction port 22c of the cooling side ejector 22 by the suction effect | action of the cooling side injection refrigerant | coolant injected from the cooling side nozzle part 22a. .

The cooling-side injection refrigerant injected from the cooling-side nozzle portion 22a and the cooling-side suction refrigerant sucked from the cooling-side refrigerant suction port 22c of the cooling-side ejector 22 flow into the cooling-side diffuser portion 22d (from i8 to j8 in FIG. 8). Point, p8 point to j8 point).

In the cooling side diffuser portion 22d, the velocity energy of the refrigerant is converted into pressure energy by expanding the refrigerant passage area. As a result, the pressure of the mixed refrigerant of the cooling-side injection refrigerant and the cooling-side suction refrigerant increases (from point j8 to point k8 in FIG. 8). The refrigerant that has flowed out of the cooling side diffuser portion 22d flows into the cooling side accumulator 23 and is separated into a gas phase refrigerant and a liquid phase refrigerant.

The liquid refrigerant (m8 point in FIG. 8) separated by the cooling-side accumulator 23 flows into the throttled sixth flow rate adjustment valve 15f and is depressurized (from m8 point to o8 point in FIG. 8). . The refrigerant depressurized by the sixth flow rate adjusting valve 15f flows from the other refrigerant inlet / outlet of the indoor evaporator 21, absorbs heat from the air blown from the blower 32, and evaporates (from point o8 to point p8 in FIG. 8). . Thereby, air is cooled.

The gas-phase refrigerant (point n8 in FIG. 8) separated by the cooling-side accumulator 23 is sucked into the compressor 11 through the second four-way valve 13b, the suction-side accumulator 24, etc. and compressed again (in FIG. 8). n8 points to a8 points).

Therefore, in the cooling mode, the air in the vehicle interior can be cooled by blowing the air cooled by the indoor evaporator 21 into the vehicle interior without being reheated by the indoor condenser 12.

Furthermore, in the cooling mode, the refrigerant whose pressure has been increased by the cooling side diffuser portion 22d of the cooling side ejector 22 is sucked into the compressor 11. Therefore, in comparison with a normal refrigeration cycle apparatus in which the refrigerant evaporation pressure in the heat exchanger functioning as an evaporator (in the cooling mode, the indoor evaporator 21) and the pressure of the refrigerant sucked in the compressor 11 are equal. 11 can be reduced, and the coefficient of performance COP of the cycle can be improved.

(B) First Dehumidification Heating Mode In the first dehumidification heating mode, the air conditioning control device 40 connects the refrigerant outlet side of the indoor condenser 12 and the first three-way joint 14a side at the same time as the second four-way valve 13b side and the third. The operation of the first four-way valve 13a is controlled so as to switch to the refrigerant circuit that connects the three-way joint 14c side. Further, the refrigerant circuit connecting the gas-phase refrigerant inlet / outlet side of the heating-side accumulator 19 and the first four-way valve 13a side is simultaneously switched to the refrigerant circuit connecting the gas-phase refrigerant inlet / outlet side of the cooling-side accumulator 23 and the inlet side of the suction-side accumulator 24. Thus, the operation of the second four-way valve 13b is controlled.

In addition, the air conditioning controller 40 sets the first flow rate adjustment valve 15a to the fully closed state, sets the second flow rate adjustment valve 15b to the throttled state, sets the third flow rate adjustment valve 15c to the fully open state, and sets the fourth flow rate adjustment valve 15d to the fully open state. The closed state is set, the fifth flow rate adjusting valve 15e is throttled, and the sixth flow rate adjusting valve 15f is fully opened. Further, the air conditioning control device 40 closes the first on-off valve 18a and closes the second on-off valve 18b.

Thereby, in the 1st dehumidification heating mode, as shown to the solid line arrow of FIG. 3, the compressor 11, the indoor condenser 12, the 2nd flow regulating valve 15b, the outdoor heat exchanger 17, (3rd flow regulating valve 15c, ) A refrigeration cycle in which refrigerant circulates in the order of the heating side accumulator 19, the fifth flow rate adjustment valve 15e, the indoor evaporator 21, the (sixth flow rate adjustment valve 15f), the cooling side accumulator 23, the suction side accumulator 24, and the compressor 11 is configured. Is done.

Therefore, in the first dehumidifying and heating mode, the indoor condenser 12, the outdoor heat exchanger 17, and the indoor evaporator 21 are connected in series to the refrigerant flow in this order.

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

For example, the throttle opening of the second flow rate adjustment valve 15b, that is, the control signal (control pulse) output to the second flow rate adjustment valve 15b is stored in advance in the air conditioning control device 40 based on the target blowing temperature TAO. Determined with reference to the control map. Specifically, the throttle opening is determined so as to decrease as the target blowing temperature TAO increases. In other words, the throttle opening is determined to decrease as the heating capacity required for the cycle increases.

Further, the throttle opening degree of the fifth flow rate adjusting valve 15e, that is, the control signal (control pulse) output to the fifth flow rate adjusting valve 15e is previously stored in the air conditioning control device 40 based on the target blowing temperature TAO. Determined with reference to the control map. Specifically, the COP of the ejector refrigeration cycle 10 is determined so as to approach the maximum value.

Therefore, the throttle opening degree of the fifth flow rate adjustment valve 15e increases as the throttle opening degree of the second flow rate adjustment valve 15b decreases. In other words, the throttle opening degree of the fifth flow rate adjusting valve 15e is determined so as to increase as the heating capacity required for the cycle increases.

As for the opening of the air mix door 34, that is, the control signal output to the electric actuator that drives the air mix door 34, the air temperature TAV detected by the air conditioning wind temperature sensor 47 approaches the target outlet temperature TAO. It is determined. The operating states of other devices to be controlled are determined in the same manner as in the cooling mode.

Therefore, in the ejector refrigeration cycle 10 in the first dehumidifying and heating mode, the state of the refrigerant changes as shown in the Mollier diagram of FIG. In the Mollier diagram of FIG. 9, the state of the refrigerant in the same place as the Mollier diagram of FIG. 8 described in the cooling mode in the cycle configuration is indicated by the same reference numerals (alphabet) as in FIG. It has changed. The same applies to other Mollier diagrams described below.

Specifically, in the first dehumidifying and heating mode, the air mix door 34 opens the air passage on the indoor condenser 12 side, so that the high-pressure refrigerant (point a9 in FIG. 9) discharged from the compressor 11 becomes the indoor condenser. 12 and heat is exchanged with a part of the air cooled and dehumidified by the indoor evaporator 21 to dissipate heat (from point a9 to point b9 in FIG. 9). Thereby, a part of air is heated.

The refrigerant that has flowed out of the indoor condenser 12 flows into the second flow rate adjusting valve 15b via the first four-way valve 13a and the like and is depressurized (from point b9 to point c9 in FIG. 9). The refrigerant decompressed by the second flow rate adjustment valve 15 b flows into one refrigerant inlet / outlet of the outdoor heat exchanger 17.

Here, when the outdoor heat exchanger temperature Tout is higher than the outdoor air temperature Tam, as shown in FIG. 9, the refrigerant flowing into the outdoor heat exchanger 17 is blown by the outdoor heat exchanger 17. The heat is radiated to the outside air blown from (from point c9 to point e9 in FIG. 9). On the other hand, when the outdoor heat exchanger temperature Tout is lower than the outdoor temperature Tam, the refrigerant flowing into the outdoor heat exchanger 17 absorbs heat from the outside air blown from the blower fan in the outdoor heat exchanger 17. .

The refrigerant flowing out from the other refrigerant inlet / outlet of the outdoor heat exchanger 17 flows into the fifth flow rate adjusting valve 15e via the heating side accumulator 19, the second four-way valve 13b, the first four-way valve 13a, etc., and is depressurized. (From point e9 to point p9 in FIG. 9).

The refrigerant decompressed by the fifth flow rate adjusting valve 15e flows into one refrigerant inlet / outlet of the indoor evaporator 21 and evaporates by exchanging heat with the air blown from the blower 32 (from point p9 to n9 in FIG. 9). ). Thereby, air is cooled. The refrigerant flowing out from the other refrigerant inlet / outlet of the indoor evaporator 21 is sucked into the compressor 11 through the cooling side accumulator 23, the second four-way valve 13b, the suction side accumulator 24, etc., and is compressed again (n9 in FIG. 9). A9 points from the point).

Accordingly, in the first dehumidifying and heating mode, the air that has been cooled and dehumidified by the indoor evaporator 21 is reheated by the indoor condenser 12 and blown out into the vehicle interior, thereby performing dehumidification heating in the vehicle interior. .

Further, in the first dehumidifying and heating mode, the temperature of the refrigerant flowing into the outdoor heat exchanger 17 is lowered than in the cooling mode by setting the first flow rate adjusting valve 15a to the throttle state. Therefore, the temperature difference between the refrigerant temperature and the outside air temperature in the outdoor heat exchanger 17 can be reduced more than in the cooling mode, and the heat radiation amount of the refrigerant in the outdoor heat exchanger 17 can be reduced as compared with the first dehumidifying and heating mode. be able to.

Thereby, compared with the case where the operation of the air mix door 34 is controlled so that the air temperature TAV approaches the target blowing temperature TAO in the cooling mode, the indoor condenser is increased without increasing the circulating refrigerant flow rate circulating in the cycle. The refrigerant | coolant pressure in 12 can be raised, and the heating capability of the air in the indoor condenser 12 can be improved.

(C) Second Dehumidification Heating Mode In the second dehumidification heating mode, the air conditioning control device 40 connects the refrigerant outlet side of the indoor condenser 12 and the third three-way joint 14c side at the same time as the second four-way valve 13b side and the first. The operation of the first four-way valve 13a is controlled so as to switch to the refrigerant circuit that connects the three-way joint 14a side. Further, the refrigerant circuit connecting the gas phase refrigerant inlet / outlet side of the heating side accumulator 19 and the inlet side of the suction side accumulator 24 is switched to the refrigerant circuit connecting the gas phase refrigerant inlet / outlet side of the cooling side accumulator 23 and the first four-way valve 13a side. Thus, the operation of the second four-way valve 13b is controlled.

In addition, the air conditioning controller 40 sets the first flow rate adjustment valve 15a to the fully closed state, sets the second flow rate adjustment valve 15b to the throttled state, sets the third flow rate adjustment valve 15c to the fully open state, and sets the fourth flow rate adjustment valve 15d to the fully open state. The closed state is set, the fifth flow rate adjusting valve 15e is throttled, and the sixth flow rate adjusting valve 15f is fully opened. Further, the air conditioning control device 40 closes the first on-off valve 18a and closes the second on-off valve 18b.

Thereby, in 2nd dehumidification heating mode, as shown to the solid line arrow of FIG. 4, the compressor 11, the indoor condenser 12, the 5th flow regulating valve 15e, the indoor evaporator 21, (6th flow regulating valve 15f) The cooling side accumulator 23, the second flow rate adjustment valve 15b, the outdoor heat exchanger 17, the (third flow rate adjustment valve 15c), the heating side accumulator 19, the suction side accumulator 24, and the compressor 11 constitute a refrigeration cycle. Is done.

Therefore, in the second dehumidifying and heating mode, the indoor condenser 12, the indoor evaporator 21, and the outdoor heat exchanger 17 are connected in series to the refrigerant flow in this order.

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

For example, the throttle opening degree of the fifth flow rate adjusting valve 15e, that is, the control signal (control pulse) output to the fifth flow rate adjusting valve 15e is stored in advance in the air conditioning control device 40 based on the target blowing temperature TAO. Determined with reference to the control map. Specifically, the throttle opening is determined so as to decrease as the target blowing temperature TAO increases. In other words, the throttle opening is determined to decrease as the heating capacity required for the cycle increases.

Further, the throttle opening degree of the second flow rate adjustment valve 15b, that is, the control signal (control pulse) output to the second flow rate adjustment valve 15b is stored in the air conditioning control device 40 in advance based on the target blowing temperature TAO. Determined with reference to the control map. Specifically, the COP of the ejector refrigeration cycle 10 is determined so as to approach the maximum value.

For this reason, the throttle opening of the second flow rate adjusting valve 15b increases as the throttle opening of the fifth flow rate adjusting valve 15e decreases. In other words, the throttle opening is determined so as to increase as the heating capacity required for the cycle increases.

As for the opening of the air mix door 34, that is, the control signal output to the electric actuator that drives the air mix door 34, the air temperature TAV detected by the air conditioning wind temperature sensor 47 approaches the target outlet temperature TAO. It is determined. The operating states of other devices to be controlled are determined in the same manner as in the cooling mode.

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

Specifically, in the second dehumidifying and heating mode, the air mix door 34 opens the air passage on the indoor condenser 12 side, so that the high-pressure refrigerant discharged from the compressor 11 (point a10 in FIG. 10) is converted into the indoor condenser. 12, the heat is exchanged with a part of the air cooled and dehumidified by the indoor evaporator 21 to dissipate heat (from point a10 to point b10 in FIG. 10). Thereby, a part of air is heated.

The refrigerant that has flowed out of the indoor condenser 12 flows into the fifth flow rate adjusting valve 15e via the first four-way valve 13a and the like, and is depressurized (from point b10 to point p10 in FIG. 10). The refrigerant decompressed by the fifth flow rate adjustment valve 15e flows into one refrigerant inlet / outlet of the indoor evaporator 21. The refrigerant flowing into the indoor evaporator 21 is evaporated by exchanging heat with the air blown from the blower 32 (from point p10 to point n10 in FIG. 10). Thereby, air is cooled.

The refrigerant flowing out from the other refrigerant inlet / outlet of the indoor evaporator 21 flows into the second flow rate adjustment valve 15b through the cooling side accumulator 23, the second four-way valve 13b, the first four-way valve 13a, etc., and is depressurized ( N10 point to c10 point in FIG. 10).

The refrigerant depressurized by the second flow rate adjustment valve 15b flows into one refrigerant inlet / outlet of the outdoor heat exchanger 17, and absorbs heat from the outside air blown from the blower fan (from point c10 to point f10 in FIG. 10). The refrigerant that has flowed out from the other refrigerant inlet / outlet of the outdoor heat exchanger 17 is sucked into the compressor 11 through the heating side accumulator 19, the second four-way valve 13b, the suction side accumulator 24, and the like (FIG. 10). f10 point to a10 point).

Therefore, in the second dehumidifying and heating mode, the air that has been cooled and dehumidified by the indoor evaporator 21 is reheated by the indoor condenser 12 and blown out into the vehicle interior, thereby performing dehumidification heating in the vehicle interior. .

In the second dehumidifying and heating mode, the outdoor heat exchanger 17 is caused to function as an evaporator, and the refrigerant evaporation pressure in the outdoor heat exchanger 17 is made lower than the refrigerant evaporation pressure in the indoor evaporator 21. Therefore, the heat radiation amount of the refrigerant in the indoor condenser 12 can be increased as compared with the first dehumidifying and heating mode.

Thereby, the refrigerant pressure in the indoor condenser 12 can be increased without increasing the circulating refrigerant flow rate circulating in the cycle with respect to the first dehumidifying heating mode. As a result, the air heating capability in the indoor condenser 12 can be improved, and the temperature of the air can be raised to a temperature range higher than that in the first dehumidifying and heating mode.

Further, as is clear from the above description, the refrigerant flow direction in the outdoor heat exchanger 17 in the first dehumidifying heating mode is the same as the refrigerant flow direction in the outdoor heat exchanger 17 in the second dehumidifying heating mode. It has become. That is, in the outdoor heat exchanger 17 in the first and second dehumidifying and heating modes, the refrigerant flows from one refrigerant inlet / outlet side toward the other refrigerant inlet / outlet side.

Furthermore, the flow direction of the refrigerant in the indoor evaporator 21 in the first dehumidifying and heating mode is the same as the flow direction of the refrigerant in the indoor evaporator 21 in the second dehumidifying and heating mode. That is, in the indoor evaporator 21 in the first and second dehumidifying and heating modes, the refrigerant flows from one refrigerant inlet / outlet side toward the other refrigerant inlet / outlet side.

Furthermore, the flow direction of the refrigerant in the indoor evaporator 21 in the first and second dehumidifying and heating modes is different from the flow direction of the refrigerant in the indoor evaporator 21 in the cooling mode. That is, in the indoor evaporator 21 in the refrigerant mode, the refrigerant flows from the other refrigerant inlet / outlet side toward the one refrigerant inlet / outlet side.

(D) Heating mode In the heating mode, the air conditioning control device 40 connects the refrigerant outlet side of the indoor condenser 12 and the first three-way joint 14a side, and simultaneously connects the second four-way valve 13b side and the third three-way joint 14c side. The operation of the first four-way valve 13a is controlled so as to switch to the refrigerant circuit to be connected. Further, the refrigerant circuit connecting the gas phase refrigerant inlet / outlet side of the heating side accumulator 19 and the inlet side of the suction side accumulator 24 is switched to the refrigerant circuit connecting the gas phase refrigerant inlet / outlet side of the cooling side accumulator 23 and the first four-way valve 13a side. Thus, the operation of the second four-way valve 13b is controlled.

In addition, the air conditioning control device 40 sets the first flow rate adjustment valve 15a to the throttle state, sets the second flow rate adjustment valve 15b to the fully closed state, sets the third flow rate adjustment valve 15c to the throttle state, and further sets the first on-off valve 18a to open.

Thereby, in the heating mode, as shown by the solid line arrow in FIG. 5, the compressor 11, the indoor condenser 12, the first flow rate adjustment valve 15 a, the heating side ejector 16, the heating side accumulator 19, the suction side accumulator 24, the compressor The ejector type refrigeration cycle in which the refrigerant circulates in the order of the heating accumulator 19, the third flow rate adjustment valve 15c, the outdoor heat exchanger 17, and the heating side refrigerant suction port 16c of the heating side ejector 16 is configured. Is done.

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

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 based on the target outlet temperature TAO with reference to a control map stored in the air conditioning control device 40 in advance.

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 so that the discharge refrigerant temperature Td approaches the target condenser temperature TCO using a feedback control method. A control signal output to the electric motor of the machine 11 is determined.

Further, the throttle opening of the first flow rate adjusting valve 15a, that is, the control signal (control pulse) output to the first flow rate adjusting valve 15a is output to the refrigerant discharge capacity of the compressor 11, for example, the electric motor of the compressor 11. Is determined with reference to a control map stored in advance in the air-conditioning control device 40 based on the control signal.

In this control map, the throttle opening degree of the first flow rate adjusting valve 15a is determined so that the dryness x of the refrigerant flowing into the heating side nozzle portion 16a is 0.5 or more and 0.8 or less. The range of the dryness x is a value obtained experimentally in advance as a value that can bring the heating capacity of air in the indoor condenser 12 close to the maximum value.

Further, the throttle opening degree of the third flow rate adjusting valve 15c, that is, the control signal (control pulse) output to the third flow rate adjusting valve 15c is determined as the reference opening degree for heating stored in the air conditioning control device 40 in advance. Is done.

Also, the control signal output to the electric actuator that drives the air mix door 34 is determined so that the total flow rate of air after passing through the indoor evaporator 21 flows through the air passage on the indoor condenser 12 side.

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

Specifically, in the heating mode, the air mix door 34 fully opens the air passage on the indoor condenser 12 side, so that the high-pressure refrigerant (point a11 in FIG. 11) discharged from the compressor 11 is transferred to the indoor condenser 12. Into the air and heat exchange with the air to dissipate heat (from point a11 to point b11 in FIG. 11). Thereby, air is heated.

The refrigerant that has flowed out of the indoor condenser 12 flows into the first flow rate adjustment valve 15a via the first four-way valve 13a and is depressurized (from point b11 to point r11 in FIG. 11). Thereby, the dryness x of the refrigerant | coolant which flows in into the heating side nozzle part 16a is adjusted to 0.5 or more and 0.8 or less.

The refrigerant decompressed by the first flow rate adjusting valve 15a flows into the heating side nozzle portion 16a of the heating side ejector 16. The refrigerant that has flowed into the heating-side nozzle portion 16a is isentropically decompressed and injected (from point r11 to point s11 in FIG. 11). The refrigerant flowing out from one refrigerant inlet / outlet of the outdoor heat exchanger 17 is sucked from the heating-side refrigerant suction port 16c of the heating-side ejector 16 by the suction action of the heating-side injected refrigerant.

The heating-side jet refrigerant injected from the heating-side nozzle portion 16a and the heating-side suction refrigerant sucked from the heating-side refrigerant suction port 16c of the heating-side ejector 16 flow into the heating-side diffuser portion 16d (from s11 to t11 in FIG. 11). Point, c11 point to t11 point).

In the heating side diffuser portion 16d, the velocity energy of the refrigerant is converted into pressure energy by expanding the refrigerant passage area. Thereby, the pressure of the mixed refrigerant of the heating side injection refrigerant and the heating side suction refrigerant rises (from the point t11 to the point u11 in FIG. 11). The refrigerant flowing out of the heating side diffuser portion 16d flows into the heating side accumulator 19 and is separated into a gas phase refrigerant and a liquid phase refrigerant.

The liquid refrigerant (point e11 in FIG. 11) separated by the heating-side accumulator 19 flows into the throttled third flow rate adjustment valve 15c and is depressurized (points e11 to d11 in FIG. 11). . The refrigerant depressurized by the third flow rate adjusting valve 15c flows from the other refrigerant inlet / outlet of the outdoor heat exchanger 17, absorbs heat from the outside air blown from the blower fan, and evaporates (from point d11 to point c11 in FIG. 11). ).

The gas-phase refrigerant (point f11 in FIG. 11) separated by the heating-side accumulator 19 is sucked into the compressor 11 via the second four-way valve 13b, the suction-side accumulator 24, etc. and compressed again (in FIG. 11). f11 point to a11 point).

Accordingly, in the heating mode, the vehicle interior can be heated by blowing the air heated by the indoor condenser 12 into the vehicle interior.

Furthermore, in the heating mode, the refrigerant whose pressure has been increased by the heating side diffuser portion 16d of the heating side ejector 16 is sucked into the compressor 11. Therefore, compared with a normal refrigeration cycle apparatus in which the refrigerant evaporation pressure in the heat exchanger functioning as an evaporator (outdoor heat exchanger 17 in the heating mode) and the pressure of the refrigerant sucked in the compressor 11 are equal. The power consumption of the machine 11 can be reduced and the COP can be improved.

Further, as is clear from the above description, the flow direction of the refrigerant in the outdoor heat exchanger 17 in the first and second dehumidifying heating modes is different from the flow direction of the refrigerant in the outdoor heat exchanger 17 in the heating mode. . That is, in the outdoor heat exchanger 17 in the heating mode, the refrigerant flows from the other refrigerant inlet / outlet side toward the one refrigerant inlet / outlet side.

Here, in the refrigerant circuit that causes the outdoor heat exchanger 17 of the ejector refrigeration cycle 10 to function as an evaporator as in the second dehumidifying heating mode or the heating mode of the ejector refrigeration cycle 10, the refrigerant evaporation of the outdoor heat exchanger 17 is performed. When the temperature is below freezing point (0 ° C. or lower), frost formation may occur in the outdoor heat exchanger 17.

When such frost formation occurs, the outdoor air passage of the outdoor heat exchanger 17 is blocked by frost, so that the heat exchange performance of the outdoor heat exchanger 17 is deteriorated. Therefore, the amount of heat absorbed by the refrigerant from the outside air in the outdoor heat exchanger 17 decreases, and the ejector refrigeration cycle 10 cannot sufficiently heat the air.

On the other hand, in the vehicle air conditioner 1 of the present embodiment, when frost formation occurs in the outdoor heat exchanger 17 of the ejector refrigeration cycle 10, an operation in a defrost mode is performed to remove the frost formation. Can do.

Specifically, in this embodiment, the outside air temperature Tam is 0 ° C. or less, and a value obtained by subtracting the outdoor heat exchanger temperature Tout from the outside air temperature Tam (Tam−Tout) is a predetermined reference temperature difference. When it is above, it determines with the outdoor heat exchanger 17 having formed frost. Then, the operation in the defrosting mode is executed until a predetermined reference time elapses. The operation in the defrosting mode will be described below.

(E) Defrost mode In the defrost mode, the air conditioning control device 40 connects the refrigerant outlet side of the indoor condenser 12 and the first three-way joint 14a side, and at the same time the second four-way valve 13b side and the third three-way joint 14c side. The operation of the first four-way valve 13a is controlled so as to switch to the refrigerant circuit connecting the two. Further, the refrigerant circuit connecting the gas phase refrigerant inlet / outlet side of the heating side accumulator 19 and the inlet side of the suction side accumulator 24 is switched to the refrigerant circuit connecting the gas phase refrigerant inlet / outlet side of the cooling side accumulator 23 and the first four-way valve 13a side. Thus, the operation of the second four-way valve 13b is controlled.

Further, the air conditioning control device 40 sets the first flow rate adjustment valve 15a to a fully closed state, sets the second flow rate adjustment valve 15b to a throttled state, sets the third flow rate adjustment valve 15c to a fully open state, and further sets the first on-off valve 18a to close.

Thereby, in defrost mode, as shown by the solid line arrow of Drawing 6, compressor 11, indoor condenser 12, 2nd flow control valve 15b, outdoor heat exchanger 17, (3rd flow control valve 15c), heating The refrigerant circulates in the order of the side accumulator 19, the suction side accumulator 24, and the compressor 11.

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

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 so that the defrosting refrigerant discharge capacity stored in the air conditioning control device 40 in advance is exhibited. The Further, the throttle opening degree of the second flow rate adjustment valve 15b, that is, the control signal (control pulse) output to the second flow rate adjustment valve 15b is the defrosting reference opening degree stored in advance in the air conditioning control device 40. To be determined.

For 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 air after passing through the indoor evaporator 21 is It is determined to flow around the condenser 12.

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

Specifically, the high-pressure refrigerant (point a12 in FIG. 12) 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 air.

The refrigerant that has flowed out of the indoor condenser 12 flows into the second flow rate adjustment valve 15b through the first four-way valve 13a and is depressurized (from point a12 to point c12 in FIG. 12). The refrigerant decompressed by the second flow rate adjusting valve 15b flows into one refrigerant inlet / outlet of the outdoor heat exchanger 17 and dissipates heat to the outdoor heat exchanger 17 (from point c12 to point f12 in FIG. 12). As a result, the outdoor heat exchanger 17 is defrosted.

The refrigerant that has flowed out of the outdoor heat exchanger 17 is fully opened through the second flow rate adjusting valve 15b, the heating side accumulator 19, the second four-way valve 13b, and the suction side accumulator 24 that are fully open. And compressed again (from point f12 to point a12 in FIG. 12).

As described above, according to the ejector refrigeration cycle 10 of the present embodiment, in the vehicle air conditioner 1, by switching to the cooling mode, the first dehumidifying heating mode, the second dehumidifying heating mode, and the heating mode, Appropriate air conditioning in the passenger compartment can be realized. Furthermore, in the ejector type refrigeration cycle 10 of the present embodiment, since it can be switched to the refrigerant circuit in the defrosting mode, this can be removed when frost formation occurs in the outdoor heat exchanger 17.

Furthermore, in the ejector refrigeration cycle 10 of the present embodiment, the temperature adjustment range of air during dehumidifying heating in the passenger compartment can be expanded.

This will be explained in more detail. In the ejector-type refrigeration cycle of the prior art, when performing dehumidification heating by connecting an outdoor heat exchanger and an indoor evaporator in series to the refrigerant flow, the ejector-type refrigeration cycle is performed. In order to operate the cycle appropriately, it was necessary to maintain the refrigerant pressure in the outdoor heat exchanger above a predetermined value. For this reason, there existed a range in which the temperature of the air blown into the vehicle compartment during the dehumidifying heating (the blown air temperature) cannot be adjusted.

Specifically, in the ejector-type refrigeration cycle of the prior art, when the outdoor heat exchanger and the indoor evaporator are switched to the refrigerant circuit connected in series to the refrigerant flow, within the range A of FIG. The blowout air temperature could be adjusted. Further, when the outdoor heat exchanger and the indoor evaporator were switched to the refrigerant circuit connected in parallel to the refrigerant flow, the blown air temperature could be adjusted within the range C in FIG.

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

On the other hand, in the ejector refrigeration cycle 10 of the present embodiment, in the first and second dehumidifying heating modes, the outdoor heat exchanger 17 and the indoor evaporator 21 are connected in series to the refrigerant flow. Switch. Therefore, the refrigerant can be reliably supplied to the outdoor heat exchanger 17 and the indoor evaporator 21 by the suction and discharge action of the compressor 11 regardless of the refrigerant pressure in the outdoor heat exchanger 17.

Further, in the first dehumidifying and heating mode, the outdoor heat exchanger 17 is arranged on the upstream side of the refrigerant flow with respect to the indoor evaporator 21 via the fifth flow rate adjusting valve 15e, which is the second decompression device. The refrigerant temperature in 17 can be adjusted in a temperature range higher than the refrigerant temperature in the indoor evaporator 21.

Therefore, the refrigerant heat dissipation amount in the indoor condenser 12 can be adjusted by adjusting the throttle opening of the fifth flow rate adjusting valve 15e and adjusting the refrigerant heat absorption / release amount in the outdoor heat exchanger 17. Thereby, in the 1st dehumidification heating mode, it turns out that the adjustment range of blowing air temperature can be expanded to the range D of FIG.

Furthermore, in the second dehumidifying and heating mode, the outdoor heat exchanger 17 is disposed downstream of the refrigerant flow with respect to the indoor evaporator 21 via the second flow rate adjustment valve 15b that is the first pressure reducing device. The refrigerant temperature in 17 can be set to a temperature range lower than the refrigerant temperature in the indoor evaporator 21.

Therefore, by adjusting the throttle opening of the second flow rate adjusting valve 15b, the heat absorption amount of the refrigerant in the outdoor heat exchanger 17 is increased, and the indoor condenser 12 has a higher heating capability than the first dehumidifying heating mode. The air can be heated. Thereby, in the 2nd dehumidification heating mode, it turns out that the adjustment range of blowing air temperature can be expanded to the range E of FIG.

As a result, according to the ejector refrigeration cycle 10 of the present embodiment, when dehumidifying and heating the vehicle interior, the first dehumidifying and heating mode and the second dehumidifying and heating mode are switched, so that the temperature of the air can be controlled in a wide temperature range. Can be adjusted.

In the ejector refrigeration cycle 10 of the present embodiment, the refrigerant flow direction in the outdoor heat exchanger 17 in the first and second dehumidifying heating modes is different from the refrigerant flow direction in the outdoor heat exchanger 17 in the heating mode. ing. According to this, the flow mode of the refrigerant in the outdoor heat exchanger 17 in the first and second dehumidifying and heating modes and the flow mode of the refrigerant in the outdoor heat exchanger 17 in the heating mode are changed to change the outdoor heat. It is possible to suppress the refrigeration oil from staying in the exchanger 17.

Specifically, in this embodiment, the passage cross-sectional area of the refrigerant passage formed inside the outdoor heat exchanger 17 is changed from the refrigerant inlet (the other refrigerant inlet / outlet) side to the refrigerant outlet (one refrigerant inlet / outlet) in the heating mode. ) Reduced toward the side. Thereby, the flow rate of the refrigerant | coolant which distribute | circulates the outdoor heat exchanger 17 at the time of heating mode can be increased, and it can suppress that refrigerating machine oil retains in the outdoor heat exchanger 17. FIG.

More specifically, the outdoor heat exchanger 17 in the heating mode functions as an evaporator. Therefore, in the refrigerant passage in the outdoor heat exchanger 17, the density of the refrigerant decreases as the liquid phase refrigerant evaporates from the refrigerant inlet side toward the refrigerant outlet side. Therefore, by reducing the passage cross-sectional area of the refrigerant passage from the refrigerant inlet side to the refrigerant outlet side of the outdoor heat exchanger 17, the flow rate of the refrigerant flowing through the outdoor heat exchanger 17 is increased, and the outdoor heat exchanger 17 The refrigerating machine oil staying in 17 can be discharged from the outdoor heat exchanger 17.

In the ejector refrigeration cycle 10 of the present embodiment, the refrigerant flow direction in the indoor evaporator 21 in the first and second dehumidifying heating modes is different from the refrigerant flow direction in the indoor evaporator 21 in the cooling mode. . According to this, the flow mode of the refrigerant in the indoor evaporator 21 in the first and second dehumidifying heating modes and the flow mode of the refrigerant in the outdoor heat exchanger 17 in the heating mode are changed to change the indoor evaporator It is possible to suppress the refrigerating machine oil from staying in 21.

More specifically, the indoor evaporator 21 in the cooling mode functions as an evaporator. Accordingly, in the refrigerant passage in the indoor evaporator 21, the density of the refrigerant is reduced by the vaporization of the liquid phase refrigerant from the refrigerant inlet side toward the refrigerant outlet side. Therefore, by reducing the cross-sectional area of the refrigerant passage from the refrigerant inlet side to the refrigerant outlet side of the indoor evaporator 21, the flow velocity of the refrigerant flowing through the indoor evaporator 21 is increased, and the inside of the indoor evaporator 21 is increased. The staying refrigeration oil can be discharged from the outdoor heat exchanger 17.

In other words, according to the ejector refrigeration cycle 10 of the present embodiment, the refrigeration oil is prevented from staying in the outdoor heat exchanger 17 and the indoor evaporator 21 in an ejector refrigeration cycle applied to an air conditioner that performs dehumidifying heating. However, the temperature adjustment range of the air blown into the air-conditioning target space during dehumidifying heating can be expanded.

(Other embodiments)
Note that the present disclosure is not limited to the above-described embodiment, and can be appropriately changed without departing from the gist of the present disclosure. Further, the above embodiments are not irrelevant to each other, and can be combined as appropriate unless the combination is clearly impossible. In addition, elements constituting each of the above embodiments are not necessarily essential except when clearly indicated as essential and when considered to be clearly essential in principle.

In each of the above embodiments, when numerical values such as the number, numerical value, quantity, range, etc. of the components are mentioned, particularly when it is clearly indicated that it is essential, and when it is clearly limited to a specific number in principle. Except for this, the numerical values of the constituent elements are not limited to a specific number. Further, in each of the above embodiments, the material, shape, positional relationship, etc. of the constituent elements are the above-described specific items unless otherwise specified and in principle limited to a specific material, shape, positional relationship, etc. It is not limited to examples.

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

When applied to a vehicle having an internal combustion engine, the vehicle air conditioner 1 may be provided with a heater core that heats air using the cooling water of the internal combustion engine as a heat source as an auxiliary air heater. Furthermore, you may apply to a stationary air conditioner, without being limited to vehicles.

Further, in the above-described embodiment, the ejector refrigeration cycle 10 that heats the air directly using the refrigerant discharged from the compressor 11 as a heat source by causing the indoor condenser 12 to exchange heat between the refrigerant discharged from the compressor 11 and air. Although demonstrated, the heating aspect of the air in the indoor condenser 12 is not limited to this.

For example, a heat medium circulation circuit that circulates the heat medium is provided, and the indoor radiator is configured as a water-refrigerant heat exchanger that exchanges heat between the refrigerant discharged from the compressor and the heat medium. A heat exchanger for heating that heats the air by exchanging heat between the heat medium heated in step 1 and air may be arranged. That is, the indoor radiator may indirectly heat the air through the heat medium using the compressor discharge refrigerant (high-pressure side refrigerant of the cycle) as a heat source.

Furthermore, when applied to a vehicle having an internal combustion engine, the heat medium circulation circuit may be circulated using the cooling water of the internal combustion engine as a heat medium. Moreover, in an electric vehicle, you may make it distribute | circulate a heat-medium circulation circuit by using the cooling water which cools a battery and an electric equipment as a heat medium.

(2) In the above-described embodiment, the example in which the passage cross-sectional area of the refrigerant passage formed in the outdoor heat exchanger 17 and the indoor evaporator 21 is changed stepwise by changing the path configuration has been described. However, the method of changing the flow mode of the refrigerant in the outdoor heat exchanger 17 and the indoor evaporator 21 in each operation mode is not limited to this. For example, the outdoor heat exchanger 17 and the indoor evaporator 21 may be configured using a plurality of types of tubes having different passage cross-sectional areas.

In the above-described embodiment, the example in which the passage cross-sectional area of the refrigerant passage formed in the outdoor heat exchanger 17 is reduced from the other refrigerant inlet / outlet side toward the one refrigerant inlet / outlet side has been described. The change in the cross-sectional area is not limited to this.

For example, the flow direction of the refrigerant in the outdoor heat exchanger 17 in the first and second dehumidifying and heating modes is different from the flow direction of the refrigerant in the outdoor heat exchanger 17 in the heating mode. If the refrigerating machine oil in the outdoor heat exchanger 17 can be discharged, the cross-sectional area of the refrigerant passage may be enlarged as it goes from the other refrigerant inlet / outlet side to the one refrigerant inlet / outlet side. That is, the refrigerant passage formed in the outdoor heat exchanger 17 may have a passage cross-sectional area that increases from the refrigerant inlet side to the refrigerant outlet side in the heating mode.

According to this, in the heating mode in which the outdoor heat exchanger 17 functions as an evaporator, the passage cross-sectional area of the refrigerant passage increases from the refrigerant inlet side to the refrigerant outlet side, so that the refrigerant is the outdoor heat exchanger. The pressure loss at the time of circulating 17 can be reduced. The same applies to the indoor evaporator 21. In other words, the refrigerant passage formed inside the indoor evaporator 21 may have a passage cross-sectional area that increases from the refrigerant inlet side to the refrigerant outlet side in the cooling mode.

(3) Each component of the ejector refrigeration cycle 10 is not limited to that disclosed in the above-described embodiment.

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

Moreover, although the above-mentioned embodiment demonstrated the example which heats air by heat-exchanging a high pressure refrigerant | coolant and air in the indoor condenser 12, it replaced with the indoor condenser 12, for example, circulates a thermal medium. A heat medium circulation circuit is provided, and the heat-circulation circuit heat exchanges heat between the high-pressure refrigerant and the heat medium, and heat exchange between the heat medium heated by the water-refrigerant heat exchanger and air. You may arrange | position the heat exchanger for heating etc. which make it heat and heat.

In the above-described embodiment, the example in which a plurality of flow rate adjustment valves and on-off valves are employed as the refrigerant circuit switching device has been described. However, the refrigerant circuit switching device is not limited to this. As long as at least the above-described refrigerant circuit in the heating mode and the refrigerant circuit in the series dehumidifying heating mode can be switched, for example, a combination of a flow rate adjustment valve that does not have a fully closed function and an on-off valve, a four-way valve, etc. May be.

Further, an integrated configuration of each component device described in the above embodiment may be adopted. For example, the first flow rate adjusting valve 15a, the heating side ejector 16, the heating side accumulator 19, and the like may be integrated (modularized). In this case, a needle-like or conical valve body is disposed in the passage of the heating-side nozzle portion 16a of the heating-side ejector 16, and the same function as that of the first flow rate adjusting valve 15a is achieved by displacing the valve body. You may make it show.

Similarly, the fourth flow rate adjusting valve 15d, the cooling side ejector 22, the cooling side accumulator 23, and the like may be integrated (modularized).

Further, an evaporation pressure adjusting valve that makes the refrigerant evaporation pressure of the indoor evaporator 21 equal to or higher than a predetermined value may be disposed on the refrigerant outlet side of the indoor evaporator 21 of the ejector refrigeration cycle 10 of each of the above-described embodiments. Good. According to this, frost formation of the indoor evaporator 21 can be more reliably prevented by the mechanical mechanism.

In the above-described embodiment, the 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. Or you may employ | adopt the mixed refrigerant | coolant etc. which mixed multiple types among these refrigerant | coolants.

(4) The example in which the valve opening degree of the first flow rate adjusting valve 15a is adjusted based on the refrigerant discharge capability of the compressor 11 during the high heating capability operation in the heating mode of the above embodiment has been described. The adjustment of the valve opening degree of the valve 15a is not limited to this.

For example, a dryness sensor that detects the dryness of the refrigerant on the outlet side of the indoor condenser 12 is provided, and the valve of the first flow rate adjustment valve 15a is set so that the detected value of the dryness sensor is 0.5 or more and 0.8 or less. The valve opening degree of the opening degree may be adjusted. Moreover, you may adjust the valve opening degree of the 1st flow regulating valve 15a so that COP of the ejector-type refrigerating cycle 10 may approach the maximum value.

(5) In the above-described embodiment, the example in which each operation mode is switched by executing the air conditioning control program has been described. However, the 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.

Claims (5)

1. An ejector refrigeration cycle applied to an air conditioner,
   A compressor (11) for compressing a refrigerant mixed with refrigerating machine oil until it becomes a high-pressure refrigerant, and discharging the high-pressure refrigerant;
   A heating heat exchanger (12) for heating air blown into the air-conditioned space using the high-pressure refrigerant as a heat source;
   A first decompression device (15b) disposed on the downstream side of the heating heat exchanger and decompressing the refrigerant;
   An outdoor heat exchanger (17) for exchanging heat between the refrigerant flowing out of the first decompression device and the outside air;
   A second decompression device (15e) disposed on the downstream side of the heating heat exchanger to decompress the refrigerant;
   A cooling heat exchanger (21) for evaporating the refrigerant flowing out of the second decompression device and cooling the air before passing through the heating heat exchanger;
   A heating-side nozzle portion (16a) that is disposed downstream of the heating heat exchanger and depressurizes the refrigerant and injects it as a heating-side injection refrigerant;
   A heating-side refrigerant suction port (16c) that sucks the refrigerant as the heating-side suction refrigerant by the suction action of the heating-side injection refrigerant, and a heating-side boosting unit that boosts the mixed refrigerant of the heating-side injection refrigerant and the heating-side suction refrigerant A heating side ejector (16) having (16d);
   A heating-side gas-liquid separator (19) for separating the refrigerant flowing out from the heating-side pressurizing unit into a gas-phase refrigerant and a liquid-phase refrigerant;
   A refrigerant circuit switching device (13a, 13b, 18a, 18b) for switching the refrigerant circuit,
   The refrigerant circuit switching device is
   In the first dehumidifying and heating mode in which the air cooled by the cooling heat exchanger is reheated by the heating heat exchanger, the refrigerant flowing out of the heating heat exchanger is changed to the first pressure reducing device, Switch to the refrigerant circuit that circulates in the order of the outdoor heat exchanger, the second pressure reducing device, the cooling heat exchanger, the compressor,
   In the second dehumidifying and heating mode in which the air cooled by the cooling heat exchanger is reheated by the heating heat exchanger, the refrigerant flowing out of the heating heat exchanger is changed to the second decompression device, Switch to the refrigerant circuit for circulating the cooling heat exchanger, the first pressure reducing device, the outdoor heat exchanger, and the compressor in this order,
   In the heating mode in which the air is heated by the heating heat exchanger, the refrigerant that has flowed out of the heating heat exchanger flows into the heating side nozzle portion, and the air that has flowed out of the heating side gas-liquid separator is discharged. Phase refrigerant is sucked into the compressor, the liquid refrigerant flowing out of the heating side gas-liquid separator is allowed to flow into the outdoor heat exchanger, and the refrigerant flowing out of the outdoor heat exchanger is sucked into the heating side refrigerant Switch to a refrigerant circuit to be sucked from the mouth,
   The refrigerant flow direction in the outdoor heat exchanger during the first dehumidifying and heating mode is the same as the refrigerant flow direction in the outdoor heat exchanger during the second dehumidifying and heating mode,
   The ejector-type refrigeration cycle in which a refrigerant flow direction in the outdoor heat exchanger in the first dehumidifying heating mode is different from a refrigerant flow direction in the outdoor heat exchanger in the heating mode.
2. A refrigerant passage is formed inside the outdoor heat exchanger,
   2. The ejector refrigeration cycle according to claim 1, wherein a passage cross-sectional area of the refrigerant passage is reduced from a refrigerant inlet side toward a refrigerant outlet side in the heating mode.
3. A cooling-side nozzle portion (22a) disposed downstream of the heating heat exchanger and depressurizing the refrigerant and injecting the refrigerant as a cooling-side injection refrigerant;
   A cooling-side refrigerant suction port (22c) for sucking refrigerant as a cooling-side suction refrigerant from the cooling-side refrigerant suction port (22c) by the suction action of the cooling-side injection refrigerant, and the cooling-side injection refrigerant and the cooling-side suction refrigerant A cooling-side ejector (22) having a cooling-side boosting part (22d) for boosting the mixed refrigerant;
   A cooling-side gas-liquid separator (23) that separates the refrigerant that has flowed out of the cooling-side pressurization unit into a gas-phase refrigerant and a liquid-phase refrigerant, and
   In the cooling mode in which the air is cooled by the cooling heat exchanger, the refrigerant circuit switching device causes the refrigerant that has flowed out of the outdoor heat exchanger to flow into the cooling-side nozzle portion, and the cooling-side gas-liquid separator The gas-phase refrigerant that has flowed out of the refrigerant is sucked into the compressor, and the liquid-phase refrigerant that has flowed out of the cooling-side gas-liquid separator flows into the cooling heat exchanger and flows out of the cooling heat exchanger. Switching to a refrigerant circuit for sucking refrigerant into the cooling-side refrigerant suction port,
   The flow direction of the refrigerant in the cooling heat exchanger in the first dehumidifying and heating mode is the same as the flow direction of the refrigerant in the cooling heat exchanger in the second dehumidifying and heating mode,
   The ejector type according to claim 1 or 2, wherein a flow direction of the refrigerant in the cooling heat exchanger in the first dehumidifying heating mode is different from a flow direction of the refrigerant in the cooling heat exchanger in the cooling mode. Refrigeration cycle.
4. An ejector refrigeration cycle applied to an air conditioner,
   A compressor (11) for compressing a refrigerant mixed with refrigerating machine oil until it becomes a high-pressure refrigerant, and discharging the high-pressure refrigerant;
   A heating heat exchanger (12) for heating air blown into the air-conditioned space using the high-pressure refrigerant as a heat source;
   A first decompression device (15b) disposed on the downstream side of the heating heat exchanger and decompressing the refrigerant;
   An outdoor heat exchanger (17) for exchanging heat between the refrigerant flowing out of the first decompression device and the outside air;
   A second decompression device (15e) disposed on the downstream side of the heating heat exchanger to decompress the refrigerant;
   A cooling heat exchanger (21) for evaporating the refrigerant flowing out of the second decompression device and cooling the air before passing through the heating heat exchanger;
   A cooling side nozzle part (22a) for depressurizing the refrigerant on the downstream side of the heating heat exchanger and injecting the refrigerant as a cooling side injection refrigerant;
   A cooling-side refrigerant suction port (22c) for sucking refrigerant as a cooling-side suction refrigerant from the cooling-side refrigerant suction port (22c) by the suction action of the cooling-side injection refrigerant, and the cooling-side injection refrigerant and the cooling-side suction refrigerant A cooling-side ejector (22) having a cooling-side boosting part (22d) for boosting the mixed refrigerant;
   A cooling-side gas-liquid separator (23) for separating the refrigerant flowing out from the cooling-side pressurization unit into a gas-phase refrigerant and a liquid-phase refrigerant;
   A refrigerant circuit switching device (13a, 13b, 18a, 18b) for switching the refrigerant circuit,
   The refrigerant circuit switching device is
   In the first dehumidifying and heating mode in which the air cooled by the cooling heat exchanger is reheated by the heating heat exchanger, the refrigerant flowing out of the heating heat exchanger is changed to the first pressure reducing device, Switch to the refrigerant circuit that circulates in the order of the outdoor heat exchanger, the second pressure reducing device, the cooling heat exchanger, the compressor,
   In the second dehumidifying and heating mode in which the air cooled by the cooling heat exchanger is reheated by the heating heat exchanger, the refrigerant flowing out of the heating heat exchanger is changed to the second decompression device, Switch to the refrigerant circuit for circulating the cooling heat exchanger, the first pressure reducing device, the outdoor heat exchanger, and the compressor in this order,
   In the cooling mode in which the air is cooled by the cooling heat exchanger, the refrigerant that has flowed out of the outdoor heat exchanger flows into the cooling-side nozzle portion and flows out of the cooling-side gas-liquid separator. Is sucked into the compressor, the liquid refrigerant flowing out of the cooling side gas-liquid separator is caused to flow into the cooling heat exchanger, and the refrigerant flowing out of the cooling heat exchanger is sucked into the cooling side refrigerant. Switch to a refrigerant circuit to be sucked from the mouth,
   The flow direction of the refrigerant in the cooling heat exchanger in the first dehumidifying and heating mode is the same as the flow direction of the refrigerant in the cooling heat exchanger in the second dehumidifying and heating mode,
   An ejector refrigeration cycle in which a refrigerant flow direction in the cooling heat exchanger in the first dehumidifying heating mode is different from a refrigerant flow direction in the cooling heat exchanger in the cooling mode.
5. A refrigerant passage is formed inside the cooling heat exchanger,
   5. The ejector refrigeration cycle according to claim 3, wherein a passage cross-sectional area of the refrigerant passage is reduced from a refrigerant inlet side toward a refrigerant outlet side in the cooling mode.
   
   

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