WO2018159321A1

WO2018159321A1 - Ejector module

Info

Publication number: WO2018159321A1
Application number: PCT/JP2018/005440
Authority: WO
Inventors: 陽一郎河本; 尾形　豪太; 押谷　洋; 龍福島; 照之堀田; 達博鈴木; 航袁; 大介櫻井; 伊藤　正博; 紘志前田
Original assignee: 株式会社デンソー
Priority date: 2017-03-02
Filing date: 2018-02-16
Publication date: 2018-09-07

Abstract

In the combining of an ejector (15) having a variable nozzle part and a variable throttle mechanism (16) as an ejector module (20), a central axis of a displacement direction in which a nozzle-side drive mechanism (54) of the ejector (15) having the variable nozzle part displaces a needle valve (53) is defined as a nozzle-side central axis CL1, a central axis of a displacement direction in which a depressurization-side drive mechanism (62) of the variable throttle mechanism (16) displaces a throttle valve (61) is defined as a depressurization-side central axis CL2, and the nozzle-side central axis CL1 and the depressurization-side drive mechanism (62) have a twisted positional relationship with each other. In addition, when viewed from one central axis among the nozzle-side central axis CL1 and the depressurization-side drive mechanism (62), a drive part corresponding to the one central axis is arranged so as to overlap with the other central axis.

Description

Ejector module

Cross-reference of related applications

This application includes Japanese Patent Application No. 2017-039252 filed on Mar. 2, 2017 and Japanese Patent Application No. 2017- filed on Jun. 21, 2017, the disclosures of which are incorporated herein by reference. Based on 121448.

The present disclosure relates to an ejector module applied to an ejector refrigeration cycle.

Conventionally, an ejector type refrigeration cycle, which is a refrigeration cycle apparatus including an ejector as a refrigerant decompression device, is known. In this type of ejector-type refrigeration cycle, the pressure of the refrigerant sucked into the compressor can be made higher than the refrigerant evaporation pressure in the evaporator by the pressurizing action of the ejector. Thereby, in an ejector type refrigeration cycle, the power consumption of a compressor can be reduced and the coefficient of performance (COP) of a cycle can be improved.

Furthermore, Patent Document 1 discloses an evaporator unit applied to an ejector refrigeration cycle. The evaporator unit disclosed in Patent Document 1 includes a branching unit, an ejector, a fixed throttle, a first evaporator, a second evaporator, and the like among components constituting an ejector refrigeration cycle (in other words, unitized or modularized). ).

More specifically, the branch part branches the flow of the high-pressure refrigerant that has flowed out of the radiator, and flows it out to the nozzle part side and the fixed throttle side of the ejector. The second evaporator is a heat exchanger that evaporates the refrigerant flowing out from the diffuser portion of the ejector by exchanging heat with the blown air blown into the air-conditioning target space and evaporates the evaporated refrigerant to the suction port side of the compressor. Let The first evaporator is a heat exchanger that evaporates the refrigerant decompressed by the fixed throttle by heat exchange with the blown air that has passed through the second evaporator, and flows the evaporated refrigerant to the refrigerant suction port side of the ejector. Let

In the evaporator unit of Patent Document 1, as described above, a part of the cycle component equipment is integrated to reduce the size and productivity of the applied ejector refrigeration cycle as a whole.

Japanese Patent No. 4259531

However, the evaporator unit of Patent Document 1 employs a fixed throttle, and further employs a fixed nozzle portion that cannot change the passage cross-sectional area of the refrigerant passage as the nozzle portion of the ejector. For this reason, when load fluctuation occurs in the applied ejector refrigeration cycle and the flow rate of the refrigerant flowing into the nozzle portion changes, the energy conversion efficiency of the ejector may decrease.

Therefore, when a load change occurs in the ejector refrigeration cycle, the ejector cannot exhibit a sufficient boosting action, or the suction action of the ejector is reduced, and an appropriate flow rate of refrigerant cannot be supplied to the evaporator. Sometimes. As a result, in the evaporator unit of Patent Document 1, when the load fluctuation occurs in the ejector refrigeration cycle, the above-described COP improvement effect cannot be obtained sufficiently.

On the other hand, Patent Document 1 may adopt a variable throttle mechanism configured to be able to change the passage cross-sectional area (that is, the throttle opening degree) instead of the fixed throttle, and the nozzle portion of the ejector. It is disclosed that a variable nozzle portion configured to be able to change the passage sectional area of the refrigerant passage may be employed.

However, when a variable throttle mechanism is used instead of the fixed throttle, a drive device for changing the throttle opening is required. The same applies to the case where a variable nozzle portion is adopted as the nozzle portion of the ejector.

This type of drive is relatively large. For this reason, a unit (or module) in which constituent devices including a variable throttle mechanism or an ejector having a variable nozzle portion are integrated is likely to be large. As a result, the downsizing effect of the ejector refrigeration cycle as a whole due to the integration of the components is impaired.

In view of the above points, an object of the present disclosure is to provide an ejector module configured such that the cross-sectional area of the passage can be changed without increasing the size of the applied ejector refrigeration cycle.

An ejector module according to a first feature example of the present disclosure includes a compressor that compresses and discharges a refrigerant, a radiator that dissipates heat from the refrigerant discharged from the compressor, a first evaporator that evaporates the refrigerant, and evaporates the refrigerant. The present invention is applicable to an ejector refrigeration cycle having a second evaporator that flows out to the suction side of the compressor. The ejector module includes a nozzle portion that decompresses and injects some of the refrigerant that has flowed out of the radiator, a decompression portion that decompresses another portion of the refrigerant that has flowed out of the radiator, and an injection from the nozzle. A body part formed with a refrigerant suction port for sucking the refrigerant from the outside by the suction action of the injected refrigerant, a pressure increasing part for increasing the pressure of the mixed refrigerant of the injection refrigerant and the suction refrigerant sucked from the refrigerant suction port, and a pressure reducing part A pressure reducing side valve body portion that changes the passage cross-sectional area, and a pressure reducing side drive portion that displaces the pressure reducing side valve body portion.

Further, the refrigerant inlet side of the first evaporator is connected to the throttle-side outlet for allowing the refrigerant to flow out from the decompression unit, and the refrigerant outlet side of the first evaporator is connected to the refrigerant suction port so that the refrigerant flows out from the pressure boosting unit. A refrigerant inlet side of the second evaporator is connected to the ejector side outlet. Further, the central axis of the displacement direction in which the decompression side drive unit displaces the decompression side valve body is defined as the decompression side center axis, and when viewed from the decompression side center axis direction, the central axis of the decompression side drive unit and the nozzle unit Is an ejector module arranged in a superposition.

According to this, since the ejector module includes the pressure reducing portion, the pressure reducing side valve body portion, and the pressure reducing side driving portion, a variable throttle mechanism can be configured.

Therefore, the throttle opening of the variable throttle mechanism can be changed according to the load fluctuation of the applied ejector refrigeration cycle. And according to load fluctuation | variation, the refrigerant | coolant flow volume which flows in into a variable throttle mechanism, and the refrigerant | coolant flow volume which flows in into a nozzle part can be adjusted appropriately. As a result, a high COP can be exhibited in the ejector refrigeration cycle regardless of load fluctuations.

Furthermore, since the ejector module includes a nozzle part, a body part, and a booster part, an ejector can be formed, and the ejector and the variable throttle mechanism can be integrated.

At this time, since the central axis of the decompression side drive unit and the nozzle unit is overlapped when viewed from the decompression side central axis direction, it is possible to suppress an increase in size of the ejector module as a whole.

More specifically, according to such an arrangement, the decompression side drive unit having a relatively large physique and the ejector formed in the shape extending in the axial direction can be arranged while being shifted in the direction of the decompression side central axis. Accordingly, the part constituting the main body of the variable aperture mechanism and the part constituting the ejector can be arranged close to each other. As a result, the increase in size of the ejector module as a whole can be suppressed.

Therefore, it is possible to provide an ejector module configured such that the passage cross-sectional area can be changed without increasing the size of the applied ejector refrigeration cycle. Furthermore, specifically, by making the pressure-reduction-side central axis and the central axis of the nozzle portion into a torsional positional relationship, it is easy to bring the part constituting the main body of the variable throttle mechanism close to the part constituting the ejector.

The ejector module according to the second feature example of the present disclosure includes a nozzle portion that decompresses and injects some of the refrigerant that has flowed out of the radiator, and depressurizes another portion of the refrigerant that has flowed out of the radiator. A decompression unit that causes the refrigerant to be sucked from the outside by a suction action of the jet refrigerant ejected from the nozzle, and a refrigerant mixture sucked from the jet refrigerant and the refrigerant sucked from the refrigerant suction port. A pressure increasing part for increasing pressure, a nozzle side valve body part for changing the passage sectional area of the nozzle part, a nozzle side driving part for displacing the nozzle side valve body part, and a pressure reducing side valve body part for changing the passage sectional area of the pressure reducing part And a pressure reducing side driving part for displacing the pressure reducing side valve body part.

Further, the refrigerant inlet side of the first evaporator is connected to the throttle-side outlet for allowing the refrigerant to flow out from the decompression unit, and the refrigerant outlet side of the first evaporator is connected to the refrigerant suction port so that the refrigerant flows out from the pressure boosting unit. A refrigerant inlet side of the second evaporator is connected to the ejector side outlet. The central axis in the displacement direction in which the nozzle-side drive unit displaces the nozzle-side valve body is defined as the nozzle-side central axis, and the central axis in the displacement direction in which the decompression-side drive unit displaces the decompression-side valve body is defined as the decompression-side central axis. And when viewed from the central axis direction of one of the nozzle side central axis and the pressure reducing side central axis, the drive unit corresponding to one central axis (that is, the valve body part is displaced in the direction of one central axis) The drive unit) and the other central axis are arranged in a superposed manner.

Since the ejector module includes a pressure reducing portion, a pressure reducing side valve body portion, and a pressure reducing side driving portion, a variable throttle mechanism can be configured. Moreover, since the nozzle part, the nozzle side valve body part, and the nozzle side drive part are provided, a variable nozzle part can be comprised.

Therefore, the throttle opening of the variable throttle mechanism and the passage cross-sectional area of the nozzle portion can be changed according to the load fluctuation of the applied ejector refrigeration cycle. And according to load fluctuation | variation, the refrigerant | coolant flow volume which flows in into a variable throttle mechanism, and the refrigerant | coolant flow volume which flows in into a nozzle part can be adjusted appropriately. As a result, a high COP can be exhibited in the ejector refrigeration cycle regardless of load fluctuations.

Furthermore, since the nozzle unit, the nozzle side valve body unit, the nozzle side drive unit, the body unit, and the booster unit are provided, an ejector including a variable nozzle unit can be configured. And an ejector and a variable aperture mechanism can be integrated.

At this time, when viewed from one central axis direction of the nozzle side central axis and the decompression side central axis, the drive unit corresponding to one central axis and the other central axis are arranged in an overlapping manner, so the entire ejector module The increase in size can be suppressed.

More specifically, according to such an arrangement, the decompression side driving unit and the nozzle side driving unit, which are relatively large in size, can be arranged while being shifted in any central axis direction. Accordingly, the part constituting the main body of the variable aperture mechanism and the part constituting the main body of the ejector can be arranged close to each other. As a result, the increase in size of the ejector module as a whole can be suppressed.

That is, the nozzle-side central axis and the pressure-reducing side central axis are in a torsional positional relationship, so that the portion constituting the main body of the variable throttle mechanism (16) and the portion constituting the main body of the ejector can be easily brought close to each other. *

It is a typical whole block diagram of the ejector-type refrigerating cycle of 1st Embodiment. It is an axial direction sectional view containing the nozzle side central axis of the ejector module of a 1st embodiment. It is an axial sectional view including the decompression side central axis of the ejector module of the first embodiment. It is a side view of the ejector module of a 1st embodiment. It is a top view of the ejector module of a 1st embodiment. It is an axial direction sectional view containing the central axis of the nozzle part of the ejector module of a 2nd embodiment. It is a top view of the ejector module of 2nd Embodiment. It is axial direction sectional drawing containing the nozzle side center axis | shaft of the ejector module of 3rd Embodiment. It is an axial sectional view including the decompression side central axis of the ejector module of the fourth embodiment. It is a typical whole block diagram of the ejector-type refrigerating cycle of 5th Embodiment. It is a typical whole block diagram of the ejector-type refrigerating cycle of 6th Embodiment. It is an axial sectional view containing the decompression side central axis of the ejector module of a 6th embodiment.

(First embodiment)
A first embodiment of the present disclosure will be described with reference to FIGS. 1 to 5. The ejector module 20 of the present embodiment is applied to an ejector refrigeration cycle 10 that is a vapor compression refrigeration cycle apparatus including an ejector as a refrigerant decompression device, as shown in the overall configuration diagram of FIG. This ejector-type refrigeration cycle 10 is applied to a vehicle air conditioner, and fulfills a function of cooling blown air that is blown into a vehicle interior that is a space to be cooled. Therefore, the fluid to be cooled in the ejector refrigeration cycle 10 is blown air.

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

Among the constituent devices of the ejector refrigeration cycle 10, the compressor 11 sucks the refrigerant and compresses and discharges it until it becomes a high-pressure refrigerant. More specifically, the compressor 11 of the present embodiment is an electric compressor that is configured by housing a fixed capacity type compression mechanism and an electric motor that drives the compression mechanism in one housing.

As this compression mechanism, various compression mechanisms such as a scroll-type compression mechanism and a vane-type compression mechanism can be employed. Further, the operation (rotation speed) of the electric motor is controlled by a control signal output from an air conditioning control device (not shown), and either an AC motor or a DC motor may be adopted.

The refrigerant inlet side of the condenser 12 a of the radiator 12 is connected to the discharge port of the compressor 11. The radiator 12 is a heat dissipation heat exchanger that radiates and cools the high-pressure refrigerant by exchanging heat between the high-pressure refrigerant discharged from the compressor 11 and the outside air (outside air) blown from the cooling fan 12c. is there.

More specifically, the radiator 12 is configured as a so-called receiver-integrated condenser having a condensing part 12a and a receiver part 12b. The condensing unit 12a is a heat exchanging unit for condensation that exchanges heat between the high-pressure gas-phase refrigerant discharged from the compressor 11 and the outside air blown from the cooling fan 12c, and dissipates the high-pressure gas-phase refrigerant to condense. . The receiver unit 12b is a refrigerant container that separates the gas-liquid refrigerant flowing out from the condensing unit 12a and stores excess liquid-phase refrigerant.

The cooling fan 12c is an electric blower whose number of rotations (amount of blown air) is controlled by a control voltage output from the air conditioning control device.

A high-pressure inlet 21 a side provided in a body part (body part) 21 of the ejector module 20 is connected to the refrigerant outlet of the receiver part 12 b of the radiator 12. The ejector module 20 is obtained by integrating (in other words, modularizing) the cycle constituent devices surrounded by the broken lines in FIG. More specifically, the ejector module 20 is obtained by integrating the branching section 14, the ejector 15, the variable aperture mechanism 16, and the like.

The branch portion 14 branches the flow of the refrigerant that has flowed out of the radiator 12, causes one of the branched refrigerant to flow out to the nozzle portion 51 side of the ejector 15, and the other branched refrigerant flows to the inlet side of the variable throttle mechanism 16. Fulfills the function of draining The branch portion 14 is formed by connecting a plurality of refrigerant passages formed inside the body portion 21 of the ejector module 20.

The ejector 15 includes a nozzle portion 51 that decompresses and injects one of the refrigerants branched at the branching portion 14, and functions as a refrigerant decompression device. Furthermore, the ejector 15 functions as a refrigerant circulation device that sucks and circulates the refrigerant from outside by the suction action of the refrigerant injected from the nozzle portion 51. More specifically, the ejector 15 sucks the refrigerant that has flowed out of the first evaporator 17 described later.

In addition, the ejector 15 converts the kinetic energy of the mixed refrigerant of the refrigerant injected from the nozzle part 51 and the refrigerant sucked from the refrigerant suction port 21b formed in the body part 21 into pressure energy. It functions as an energy conversion device that boosts the pressure of the mixed refrigerant. The ejector 15 causes the pressurized refrigerant to flow out to the refrigerant inlet side of the second evaporator 18 described later. Moreover, the nozzle part 51 of the ejector 15 is comprised so that a passage cross-sectional area can be changed.

The variable throttle mechanism 16 has a throttle passage 20a that depressurizes the other refrigerant branched by the branching section 14. The variable throttle mechanism 16 is configured to be able to change the passage cross-sectional area (that is, the throttle opening) of the throttle passage 20a. The variable throttle mechanism 16 causes the decompressed refrigerant to flow out to the refrigerant inlet side of the first evaporator 17.

Next, a detailed configuration of the ejector module 20 will be described with reference to FIGS. 2 to 5 in addition to FIG. The up and down arrows in FIGS. 2 to 4 indicate the up and down directions in a state where the ejector refrigeration cycle 10 is mounted on the vehicle air conditioner. The same applies to the following drawings. 2 is a cross-sectional view taken along the line II-II in FIGS. 4 and 5, and FIG. 3 is a cross-sectional view taken along the line III-III in FIGS. 4 is a view in the direction of arrow IV in FIG. FIG. 5 is a view in the direction of arrow V in FIG.

For simplification of illustration and clarification of explanation, the refrigerant flow direction in the ejector 15 shown in the overall configuration diagram of FIG. 1 is different from the refrigerant flow direction in the ejector 15 shown in FIGS. It has become.

The body part 21 is formed by combining a plurality of structural members made of metal (in this embodiment, made of aluminum). The body portion 21 forms the outer shell of the ejector module 20 and functions as a housing that accommodates components such as the ejector 15 and the variable throttle mechanism 16 therein. The body part 21 may be formed of resin.

Various coolant passages 20a to 20c are formed in the body portion 21. The body portion 21 is provided with a plurality of refrigerant inlets and outlets such as a high pressure inlet 21a, a refrigerant suction port 21b, a throttle side outlet 21d, a low pressure inlet 21e, and a low pressure outlet 21f. Further, an ejector side outlet 21c is provided at the most downstream part of the refrigerant flow of a diffuser portion 52 of the ejector 15 described later, which is fixed to the body portion 21.

As shown in FIG. 3, the high-pressure inlet 21 a is a refrigerant inlet through which the refrigerant flowing out from the refrigerant outlet of the receiver 12 b of the radiator 12 flows into the ejector module 20. Accordingly, the high-pressure inlet 21 a serves as a refrigerant inlet for the branch portion 14.

As shown in FIG. 3, the refrigerant suction port 21 b is a refrigerant inlet that sucks the refrigerant that has flowed out of the first evaporator 17. The suction refrigerant sucked from the refrigerant suction port 21 b merges with the jet refrigerant jetted from the nozzle portion 51. Accordingly, the refrigerant passage through which the suction refrigerant sucked from the refrigerant suction port 21b is circulated and merged with the injection refrigerant is the suction-side passage 20b.

The ejector-side outlet 21c is a refrigerant outlet that causes the refrigerant whose pressure has been increased by the diffuser portion 52 to flow out to the inlet side of the second evaporator 18. As shown in FIG. 3, the throttle-side outlet 21 d is a refrigerant outlet that allows the refrigerant decompressed by the variable throttle mechanism 16 to flow out to the inlet side of the first evaporator 17.

The low-pressure inlet 21e is a refrigerant inlet through which the refrigerant that has flowed out of the second evaporator 18 flows, as shown in FIG. As shown in FIG. 2, the low-pressure outlet 21 f is a refrigerant outlet that allows the refrigerant flowing from the low-pressure inlet 21 e to flow out to the suction port side of the compressor 11. Therefore, the refrigerant passage from the low pressure inlet 21e to the low pressure outlet 21f is the outflow side passage 20c.

Furthermore, as shown in FIGS. 2 to 4, the high-pressure inlet 21a and the low-pressure outlet 21f are open in the same direction on the same plane. The ejector side outlet 21c, the low pressure inlet 21e, the refrigerant suction port 21b, and the throttle side outlet 21d open in the same direction. The low pressure inlet 21e, the refrigerant suction port 21b, and the throttle side outlet 21d are open on the same plane. Here, the refrigerant inlet / outlet opening in the same direction means that the refrigerant inflow / outflow directions coincide with each other.

2 and 3, the ejector 15 includes a nozzle portion 51, a refrigerant suction port 21b and a suction side passage 20b formed in the body portion 21, a diffuser portion 52, a needle valve 53, a nozzle side drive mechanism 54, and the like. It is configured.

The nozzle portion 51 is an isentropic decompression of the refrigerant in the refrigerant passage formed therein and injects it. As shown in FIG. 2, the nozzle portion 51 is formed of a substantially cylindrical metal (in this embodiment, stainless alloy or brass) that tapers in the refrigerant flow direction. The nozzle part 51 is fixed to the body part 21 by means such as press fitting.

In the refrigerant passage formed inside the nozzle portion 51, a throat portion having the smallest refrigerant passage area is formed, and further, the refrigerant passage area gradually increases from the throat portion toward the refrigerant injection port for injecting the refrigerant. A divergent section is provided. That is, the nozzle part 51 is configured as a Laval nozzle.

Furthermore, in the present embodiment, the nozzle unit 51 is set such that the flow rate of the injected refrigerant injected from the refrigerant injection port is equal to or higher than the speed of sound during normal operation of the ejector refrigeration cycle 10. Of course, you may comprise the nozzle part 51 by a tapered nozzle.

In the cylindrical side surface of the nozzle portion 51, an inlet hole through which one refrigerant branched by the branch portion 14 flows into the refrigerant passage is formed. The suction side passage 20b described above is formed so as to guide the suction refrigerant to the space on the outer peripheral side of the nozzle portion 51 so that the refrigerant suction port 21b and the refrigerant injection port of the nozzle portion 51 communicate with each other.

The diffuser unit 52 is a pressure increasing unit that increases the pressure of the mixed refrigerant. The diffuser part 52 is formed of a cylindrical metal (in this embodiment, aluminum). The diffuser portion 52 of the present embodiment is fixed to the body portion 21 by means such as press fitting. Of course, the diffuser portion 52 may be formed integrally with the same member as the body portion 21.

The refrigerant passage formed in the diffuser portion 52 has a substantially truncated cone shape in which the passage cross-sectional area gradually increases toward the downstream side of the refrigerant flow. In the diffuser part 52, the kinetic energy of the mixed refrigerant flowing through the diffuser part 52 is converted into pressure energy by such a passage shape.

Further, the diffuser portion 52 protrudes from the body portion 21 toward the downstream side of the refrigerant flow. Therefore, the ejector side outlet 21c formed in the most downstream portion of the refrigerant flow of the diffuser portion 52 is a plane different from the refrigerant suction port 21b, the throttle side outlet 21d, and the low pressure inlet 21e, as shown in FIGS. Open on top.

The needle valve 53 is a nozzle-side valve body portion that changes the cross-sectional area of the refrigerant passage formed inside the nozzle portion 51.

The needle valve 53 is formed in a needle shape (or a shape combining a conical shape, a cylindrical shape, etc.). The central axis of the needle valve 53 is arranged coaxially with the central axis of the nozzle part 51 and the central axis of the refrigerant passage of the diffuser part 52. The needle valve 53 changes the cross-sectional area of the refrigerant passage of the nozzle portion 51 by being displaced in the central axis direction. Further, the nozzle part 51 can be closed by bringing the needle valve 53 into contact with the throat part of the nozzle part 51.

The nozzle side drive mechanism 54 is a nozzle side drive unit that displaces the needle valve 53 in the central axis direction of the nozzle unit 51. The nozzle side drive mechanism 54 is configured by a mechanical mechanism.

More specifically, the nozzle-side drive mechanism 54 has a nozzle-side deformable member (specifically, a nozzle-side diaphragm 54b) that deforms according to the temperature and pressure of the refrigerant that has flowed out of the second evaporator 18. A side temperature sensing part 54a is provided. Then, by transmitting the deformation of the diaphragm 54b to the needle valve 53, the needle valve 53 is displaced.

The nozzle-side diaphragm 54b forms an enclosed space 54c in which a temperature-sensitive medium whose pressure changes with temperature change is enclosed in the nozzle-side temperature sensing portion 54a. In the present embodiment, the temperature-sensitive medium is mainly composed of a refrigerant circulating in the ejector refrigeration cycle 10.

The nozzle side temperature sensing portion 54a is disposed in a space formed in the body portion 21 and communicating with the outflow side passage 20c. For this reason, the pressure of the temperature-sensitive medium in the enclosed space 54c changes according to the temperature of the low-pressure refrigerant (that is, the refrigerant that has flowed out of the second evaporator 18) that flows through the outflow side passage 20c. And the diaphragm 54b deform | transforms according to the pressure difference of the pressure of the low pressure refrigerant | coolant which distribute | circulates the outflow side channel | path 20c, and the pressure of the temperature sensitive medium in the enclosure space 54c.

Therefore, it is desirable that the diaphragm 54b is formed of a material that is rich in elasticity and excellent in pressure resistance and airtightness. Therefore, in this embodiment, a circular metal thin plate made of stainless steel (SUS304) is adopted as the diaphragm 54b.

Furthermore, in the nozzle side drive mechanism 54 of the present embodiment, a part of the diaphragm 54b is fixed to the body portion 21, and the needle valve 53 is fixed to a case that forms an enclosed space 54c together with the diaphragm 54b.

Therefore, when the temperature (superheat degree) of the low-pressure refrigerant flowing through the outflow side passage 20c rises, the saturation pressure of the temperature sensitive medium in the enclosed space 54c rises, and the outflow side passage from the pressure of the temperature sensitive medium in the enclosed space 54c. The pressure difference obtained by subtracting the pressure of the low-pressure refrigerant flowing through 20c increases. Thereby, the diaphragm 54b deform | transforms into the side by which the enclosure space 54c swells. As a result, the needle valve 53 is displaced to the side that enlarges the passage cross-sectional area of the nozzle portion 51 (that is, the side away from the throat).

On the other hand, when the temperature (degree of superheat) of the low-pressure refrigerant flowing through the outflow side passage 20c decreases, the saturation pressure of the temperature sensitive medium in the enclosed space 54c decreases, and the outflow side passage from the pressure of the temperature sensitive medium in the enclosed space 54c. The pressure difference obtained by subtracting the pressure of the low-pressure refrigerant flowing through 20c becomes small. Thereby, the diaphragm 54b deform | transforms into the side in which the enclosure space 54c shrinks. As a result, the needle valve 53 is displaced to the side that reduces the cross-sectional area of the nozzle portion 51 (that is, the side that approaches the throat).

That is, the nozzle side drive mechanism 54 can displace the needle valve 53 according to the degree of superheat of the refrigerant that has flowed out of the second evaporator 18. Therefore, the nozzle side drive mechanism 54 of the present embodiment is configured so that the superheat degree of the refrigerant on the outlet side of the second evaporator 18 approaches a predetermined nozzle side reference superheat degree (specifically, 1 ° C.). Is displaced.

The nozzle side drive mechanism 54 has a coil spring that is an elastic member that applies a load on the side on which the needle valve 53 reduces the passage sectional area of the nozzle portion 51 to the nozzle side temperature sensing portion 54a. The nozzle-side reference superheat degree can be adjusted by changing the load of the coil spring.

Here, if the nozzle-side drive mechanism 54 defines the center axis in the displacement direction for displacing the needle valve 53 as the nozzle-side center axis CL1, the nozzle-side center axis CL1 is the center axis of the nozzle portion 51 and the center of the needle valve 53. The axis coincides with the central axis of the diffuser portion 52.

As shown in FIG. 3, the variable throttle mechanism 16 includes a throttle passage 20a, a throttle valve 61, a pressure reducing side drive mechanism 62, and the like.

The throttle passage 20a is a decompression section that decompresses the other refrigerant branched by the branch section 14 by reducing the passage cross-sectional area. The throttle passage 20a is formed in a rotating body shape such as a columnar shape or a truncated cone shape. The decompression part of this embodiment is formed integrally with the body part 21. Of course, an orifice formed as a separate member with respect to the body portion 21 may be adopted as the pressure reducing portion and fixed to the body portion 21 by means such as press fitting.

The throttle valve 61 is formed in a spherical shape, and is a pressure-reducing valve body portion that changes the cross-sectional area (that is, the throttle opening) of the throttle passage 20a by being displaced in the central axis direction of the throttle passage 20a. Furthermore, the throttle passage 20a can be closed by bringing the throttle valve 61 into contact with the outlet of the throttle passage 20a.

The pressure reducing side driving mechanism 62 is a pressure reducing side driving unit that displaces the throttle valve 61 in the central axis direction of the throttle passage 20a. The decompression side drive mechanism 62 is configured by a mechanical mechanism similar to the nozzle side drive mechanism 54.

More specifically, the decompression-side drive mechanism 62 includes a decompression-side deformation member (specifically, a decompression-side diaphragm 62b) that deforms according to the temperature and pressure of the refrigerant that has flowed out of the first evaporator 17. A side temperature sensing part 62a is provided. Then, by transmitting the deformation of the diaphragm 62b to the throttle valve 61, the throttle valve 61 is displaced.

In the decompression side drive mechanism 62, a part of the decompression side temperature sensing unit 62a is disposed in the suction side passage 20b. Further, in the pressure reducing side drive mechanism 62 of the present embodiment, the displacement of the diaphragm 62 b is transmitted to the throttle valve 61 via the operating rod 63. The operating rod 63 is formed in a cylindrical shape extending in the displacement direction of the throttle valve 61.

When the temperature (superheat degree) of the low-pressure refrigerant flowing through the suction side passage 20b rises, the saturation pressure of the temperature sensitive medium in the enclosed space 62c of the decompression side drive mechanism 62 rises, and the temperature sensitive medium in the enclosed space 62c. The pressure difference between the pressures of the low-pressure refrigerant flowing through the suction side passage 20b increases. As a result, when the diaphragm 62b is deformed, the throttle valve 61 is displaced to the side of increasing the throttle opening of the throttle passage 20a.

On the other hand, when the temperature (superheat degree) of the low-pressure refrigerant flowing through the suction side passage 20b is lowered, the saturation pressure of the temperature sensitive medium in the enclosed space 62c is lowered, and the suction side passage is determined from the pressure of the temperature sensitive medium in the enclosed space 62c. The pressure difference of the pressure of the low-pressure refrigerant flowing through 20b is reduced. Thus, when the diaphragm 62b is deformed, the throttle valve 61 is displaced to the side that reduces the throttle opening of the throttle passage 20a.

That is, the decompression side drive mechanism 62 can displace the throttle valve 61 according to the degree of superheat of the refrigerant flowing out from the first evaporator 17. Therefore, the nozzle-side drive mechanism 54 of the present embodiment has the throttle valve 61 so that the degree of superheat of the outlet-side refrigerant of the first evaporator 17 approaches a predetermined decompression-side reference superheat degree (specifically, 0 ° C.). Is displaced. That is, the nozzle side drive mechanism 54 of this embodiment displaces the throttle valve 61 so that the outlet side refrigerant of the first evaporator 17 becomes a saturated gas phase refrigerant.

Note that the decompression-side reference superheat degree can also be adjusted by changing the load of the coil spring, which is an elastic member that applies a load to the throttle valve 61, similarly to the nozzle-side reference superheat degree.

Here, if the pressure reducing side drive mechanism 62 defines the central axis in the displacement direction for displacing the throttle valve 61 as the pressure reducing side central axis CL2, the pressure reducing side central axis CL2 is the center axis of the throttle passage 20a and the center of the operating rod 63. Coincides with the axis.

Furthermore, in the ejector module 20 of the present embodiment, the nozzle-side central axis CL1 and the pressure-reducing side central axis CL2 have a twisted positional relationship, and one of the nozzle-side central axis CL1 and the pressure-reducing side central axis CL2 is in the direction of the central axis. When viewed from the above, the drive unit corresponding to one central axis and the other central axis are arranged in an overlapping manner.

For example, as shown in FIG. 4, when viewed from the direction of the nozzle side central axis CL1, the nozzle side drive mechanism 54 occupying the area indicated by the point hatching in FIG. 4 and the pressure reduction side central axis CL2 are arranged so as to overlap. Yes. Further, as shown in FIG. 5, when viewed from the direction of the pressure-reducing central axis CL2, the pressure-reducing driving mechanism 62 and the nozzle-side central axis CL1 occupying the region indicated by the point hatching in FIG. Yes.

Note that the torsional positional relationship means a positional relationship in which two straight lines are not parallel and do not intersect. Furthermore, in the present embodiment, the angle formed by the nozzle side central axis CL1 and the pressure reducing side central axis CL2, that is, the angle formed by the vector of the nozzle side central axis CL1 and the vector of the pressure reducing side central axis CL2 is 90 °.

Next, the second evaporator 18 shown in FIG. 1 includes the blown air blown from the blower 18a toward the vehicle interior and the ejector side outlet 21c of the ejector module 20 (that is, the refrigerant outlet of the diffuser portion 52 of the ejector 15). It is a heat-absorbing heat exchanger that cools blown air by exchanging heat with the low-pressure refrigerant that has flowed out of the air and evaporating the low-pressure refrigerant to exhibit an endothermic effect.

The blower 18a is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the air conditioning control device. The refrigerant outlet of the second evaporator 18 is connected to the low pressure inlet 21 e side of the ejector module 20.

The first evaporator 17 exchanges heat between the blown air that has passed through the second evaporator 18 and the low-pressure refrigerant that has flowed out from the throttle-side outlet 21d of the ejector module 20 (that is, the refrigerant outlet of the variable throttle mechanism 16). This is an endothermic heat exchanger that cools blown air by evaporating the refrigerant to exhibit an endothermic effect. The refrigerant outlet of the first evaporator 17 is connected to the refrigerant suction port 21 b side of the ejector module 20.

Further, the first evaporator 17 and the second evaporator 18 of the present embodiment are integrally configured. Specifically, each of the first evaporator 17 and the second evaporator 18 includes a plurality of tubes that circulate the refrigerant, and a collection or distribution of refrigerants that are arranged on both ends of the plurality of tubes and circulate through the tubes. And a so-called tank-and-tube heat exchanger having a pair of collective distribution tanks.

The first evaporator 17 and the second evaporator 18 are integrated by forming the collective distribution tank of the first evaporator 17 and the second evaporator 18 with the same member. At this time, in the present embodiment, the first evaporator 17 and the second evaporator 18 are changed to the blown air flow so that the second evaporator 18 is arranged on the upstream side of the blower air flow with respect to the first evaporator 17. In contrast, they are arranged in series. Accordingly, the blown air flows as shown by the arrows drawn by the two-dot chain line in FIG.

Furthermore, in the present embodiment, the first evaporator 17 and the second evaporator 18 integrated with the refrigerant inlets and outlets 21b to 21e of the ejector module 20 are connected using a dedicated collective pipe 19. . A plurality of metal refrigerant pipes or plate members of the collective pipe 19 are integrated by a joining means such as brazing. The collective pipe 19 has first to fourth connection passages 19a to 19d.

The first connection passage 19 a is a refrigerant passage that connects the throttle-side outlet 21 d of the ejector module 20 and the refrigerant inlet of the first evaporator 17. The second connection passage 19b is a refrigerant passage that connects the refrigerant outlet of the first evaporator 17 and the refrigerant suction port 21b. The third connection passage 19c is a refrigerant passage that connects the refrigerant inlet of the second evaporator 18 of the ejector side outlet 21c. The fourth connection passage 19d is a refrigerant passage that connects the refrigerant outlet of the second evaporator 18 and the low-pressure inlet 21e.

Furthermore, in this embodiment, as shown in FIG. 1, the site | part which protruded from the body part 21 of the diffuser part 52 is accommodated in the 3rd connection channel | path 19c. In other words, the diffuser part 52 is formed so as to be accommodated in the collective pipe 19 by protruding from the body part 21.

For this reason, the ejector module 20 is integrated with the first evaporator 17 and the second evaporator 18 via the collecting pipe 19. That is, in the present embodiment, the ejector module 20, the collecting pipe 19, the first evaporator 17 and the second evaporator 18 are integrated as an evaporator unit 200.

Next, the electric control unit of the ejector refrigeration cycle 10 of this embodiment will be described. An air conditioning control device (not shown) is composed of a well-known microcomputer including a CPU, ROM, RAM, etc. and its peripheral circuits, and performs various calculations and processing based on a control program stored in the ROM, and is connected to the output side. The operation of the various controlled

devices

11, 12c, 18a and the like is controlled.

Further, the air conditioning control device includes an inside air temperature sensor that detects the temperature inside the vehicle, an outside air temperature sensor that detects the outside air temperature, a solar radiation sensor that detects the amount of solar radiation in the vehicle interior, and the temperature of the air blown out from the first evaporator 17. Sensor groups such as an evaporator temperature sensor for detecting (evaporator temperature) are connected, and detection values of these air conditioning sensor groups are input.

Furthermore, an operation panel (not shown) is connected to the input side of the air conditioning control device, and operation signals from various operation switches provided on the operation panel are input to the air conditioning control device. As various operation switches provided on the operation panel, an air conditioning operation switch that requests air conditioning, a vehicle interior temperature setting switch that sets the vehicle interior temperature, and the like are provided.

Note that the air conditioning control device of the present embodiment is configured such that a control unit that controls the operation of various control target devices connected to the output side is integrally configured. A configuration (hardware and software) for controlling the operation of the device constitutes a control unit of each control target device. For example, in this embodiment, the structure which controls the action | operation of the compressor 11 comprises the discharge capability control part.

Next, the operation of the ejector refrigeration cycle 10 of the present embodiment having the above configuration will be described. When the air conditioning operation switch on the operation panel is turned on (ON), the air conditioning control device operates the compressor 11, the cooling fan 12c, the blower 18a, and the like.

Thereby, the compressor 11 sucks the refrigerant, compresses it, and discharges it. The high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the radiator 12. The refrigerant flowing into the radiator 12 is condensed by exchanging heat with the outside air blown from the cooling fan 12c in the condensing unit 12a. The refrigerant cooled by the condensing unit 12a is gas-liquid separated by the receiver unit 12b.

The liquid phase refrigerant separated by the receiver unit 12b flows into the high-pressure inlet 21a of the ejector module 20. The refrigerant that has flowed into the ejector module 20 is branched at the branching section 14. One of the branched refrigerant flows into the nozzle portion 51 of the ejector 15 and is isentropically decompressed and injected. And the refrigerant | coolant which flowed out from the 1st evaporator 17 is attracted | sucked from the refrigerant | coolant suction port 21b by the suction effect | action of this injection refrigerant | coolant.

At this time, the nozzle side drive mechanism 54 determines that the degree of superheat of the refrigerant flowing through the outflow side passage 20c (in other words, the outlet side refrigerant of the second evaporator 18) is the nozzle side reference superheat degree (specifically, 1 ° C.). The needle valve 53 is displaced so as to approach.

The injection refrigerant injected from the nozzle part 51 and the suction refrigerant sucked from the refrigerant suction port 21b flow into the diffuser part 52 of the ejector 15. In the diffuser part 52, 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 injection refrigerant and the suction refrigerant increases. The refrigerant whose pressure has been increased in the diffuser section 52 flows out from the ejector side outlet 21c.

The refrigerant that has flowed out of the ejector side outlet 21c flows into the second evaporator 18 through the third connection passage 19c of the collecting pipe 19. The refrigerant flowing into the second evaporator 18 absorbs heat from the blown air blown by the blower 18a and evaporates. Thereby, the blowing air blown by the blower 18a is cooled.

The refrigerant that has flowed out of the second evaporator 18 is sucked into the compressor 11 through the fourth connection passage 19d of the collecting pipe 19 and the outflow side passage 20c of the ejector module 20, and is compressed again.

On the other hand, the other refrigerant branched by the branching section 14 flows into the throttle passage 20a of the variable throttle mechanism 16 and is decompressed in an enthalpy manner. At this time, the decompression side drive mechanism 62 has a superheat degree of the suction side passage 20b (in other words, an outlet side refrigerant of the first evaporator 17) having a decompression side reference superheat degree (specifically, 0 ° C.). The throttle valve 61 is displaced so as to approach. The refrigerant decompressed by the variable throttle mechanism 16 flows out from the throttle-side outlet 21d.

The refrigerant that has flowed out of the throttle-side outlet 21d flows into the first evaporator 17 through the first connection passage 19a of the collecting pipe 19. The refrigerant flowing into the first evaporator 17 absorbs heat from the blown air after passing through the second evaporator 18 and evaporates. Thereby, the blown air after passing through the second evaporator 18 is further cooled. The refrigerant flowing out from the first evaporator 17 is sucked from the refrigerant suction port 21b through the second connection passage 19b of the collecting pipe 19.

As described above, according to the ejector refrigeration cycle 10 of the present embodiment, the blown air blown into the vehicle compartment can be cooled by the first evaporator 17 and the second evaporator 18.

Furthermore, in the ejector refrigeration cycle 10 of the present embodiment, the refrigerant on the downstream side of the second evaporator 18, that is, the refrigerant whose pressure has been increased by the diffuser portion 52 of the ejector 15 can be sucked into the compressor 11. Therefore, in the ejector-type refrigeration cycle 10, the power consumption of the compressor 11 is reduced and the coefficient of performance (COP) of the cycle is reduced as compared with a normal refrigeration cycle apparatus in which the refrigerant evaporation pressure in the evaporator is equal to the suction refrigerant pressure. Can be improved.

In the ejector refrigeration cycle 10 of the present embodiment, the refrigerant evaporation pressure in the second evaporator 18 is set to the refrigerant pressure increased by the diffuser unit 52, and the refrigerant evaporation pressure in the first evaporator 17 is set by the nozzle unit 51. A low refrigerant pressure immediately after depressurization can be achieved. Therefore, the temperature difference between the refrigerant evaporation temperature and the blown air in each evaporator can be secured and the blown air can be efficiently cooled.

Further, in the ejector module 20 of the present embodiment, the ejector 15 having the variable nozzle portion constituted by the nozzle portion 51, the needle valve 53, the nozzle side drive mechanism 54, and the like, the throttle passage 20a, the throttle valve 61, the decompression side drive. A variable diaphragm mechanism 16 constituted by a mechanism 62 or the like is provided.

Therefore, the flow rate of the refrigerant flowing into the nozzle portion 51 and the variable throttle are changed by changing the passage sectional area of the nozzle portion 51 of the ejector 15 and the throttle opening of the variable throttle mechanism 16 according to the load fluctuation of the ejector refrigeration cycle 10. The flow rate of the refrigerant flowing into the mechanism 16 can be adjusted appropriately. As a result, the ejector refrigeration cycle 10 can exhibit a high COP regardless of load fluctuations.

Furthermore, in the ejector module 20 of the present embodiment, since the branch portion 14, the ejector 15 having the variable nozzle portion, and the variable throttle mechanism 16 are integrated in the cycle constituting mechanism, the ejector refrigeration cycle 10 as a whole is integrated. It can aim for miniaturization and productivity improvement.

However, the ejector 15 having the variable nozzle portion and the variable throttle mechanism 16 require a driving device (in this embodiment, the nozzle side driving mechanism 54 and the pressure reducing side driving mechanism 62) for changing the passage cross-sectional area or the throttle opening. It becomes. Such a drive device is relatively large in size as compared with the needle valve 53, the throttle valve 61, and the like. For this reason, it becomes difficult to obtain the downsizing effect of the ejector module 20 as a whole.

On the other hand, according to the ejector module 20 of the present embodiment, when the variable throttle mechanism 16 and the ejector 15 are integrated, the nozzle-side central axis CL1 and the pressure-reducing side central axis CL2 are viewed from one central axis direction. When viewed, the drive unit corresponding to one central axis and the other central axis are arranged so as to overlap.

According to such arrangement, the decompression side driving mechanism 62 and the nozzle side driving mechanism 54 having relatively large physique can be arranged while being shifted in the direction of any of the central axes CL1 and CL2. Therefore, the main body portion (that is, the portion excluding the decompression side driving mechanism 62) of the variable throttle mechanism 16 and the main body portion of the ejector 15 (that is, the portion excluding the nozzle side driving mechanism 54) can be arranged close to each other.

Furthermore, since the nozzle-side central axis CL1 and the pressure-reducing side central axis CL2 are in a twisted positional relationship, the main body of the variable throttle mechanism 16 does not interfere with the pressure-reducing side driving mechanism 62 and the nozzle-side driving mechanism 54. And the main body of the ejector 15 can be brought close to each other effectively. Therefore, according to the ejector module 20 of the present embodiment, the applied ejector refrigeration cycle 10 is not increased in size even if the passage cross-sectional area can be changed.

Further, in the ejector module 20 of the present embodiment, the outflow side passage 20c is formed in the body portion 21, and a part of the nozzle side temperature sensing portion 54a of the nozzle side drive mechanism 54 communicates with the outflow side passage 20c. Is placed inside.

According to this, the nozzle side temperature sensing part 54a and the outflow side passage 20c can be brought close to each other. Therefore, the temperature and pressure of the refrigerant flowing through the outflow side passage 20c can be accurately transmitted to the nozzle side temperature sensing portion 54a without causing an increase in the size of the ejector module 20.

Further, in the ejector module 20 of the present embodiment, the suction side passage 20b is formed in the body portion 21, and a part of the pressure reduction side temperature sensing portion 62a of the pressure reduction side drive mechanism 62 is disposed in the suction side passage 20b. ing.

According to this, the decompression side temperature sensing part 62a and the suction side passage 20b can be brought close to each other. Therefore, the temperature and pressure of the refrigerant flowing through the suction side passage 20b can be accurately transmitted to the decompression side temperature sensing unit 62a without causing an increase in the size of the ejector module 20.

Further, in the ejector module 20 of the present embodiment, the decompression side drive mechanism 62 displaces the throttle valve 61 so that the degree of superheat of the outlet side refrigerant of the first evaporator 17 approaches 0 ° C. According to this, it can suppress that the dryness of the refrigerant | coolant which flows out out of the 1st evaporator 17 falls too much, and the gas-liquid two-phase refrigerant | coolant with a low dryness will be attracted | sucked from the refrigerant | coolant suction opening 21b. . Accordingly, it is possible to suppress a decrease in the boosting performance of the ejector 15.

Furthermore, it suppresses that the superheat degree of the refrigerant | coolant of the 1st evaporator 17 exit side raises too much, and suppresses that temperature distribution arises in the ventilation air cooled with the 1st evaporator 17. Can do. This is because, in the configuration in which the first evaporator 17 is arranged on the downstream side of the air flow of the second evaporator 18 as in the ejector refrigeration cycle 10 of the present embodiment, the temperature of the blown air as the entire ejector refrigeration cycle 10. This is effective in that the distribution is easily suppressed.

Further, in the ejector module 20 of the present embodiment, at least a part of the diffuser portion 52 protrudes from the body portion 21 and is accommodated inside the collective piping 19. According to this, in the ejector type refrigeration cycle 10, by adopting the collective pipe 19 having an appropriate shape according to the relative positional relationship between the ejector module 20 and the second evaporator 18, the ejector type refrigeration cycle 10 is further increased. Can be miniaturized.

Further, in the ejector module 20 of the present embodiment, the high pressure inlet 21a and the low pressure outlet 21f of the body portion 21 are opened in the same direction. Further, the ejector side outlet 21c, the low pressure inlet 21e, the refrigerant suction port 21b, and the throttle side outlet 21d open in the same direction.

According to this, the ejector side outlet 21c, the low pressure inlet 21e, the refrigerant suction port 21b, and the throttle side outlet 21d connected to the integrated first evaporator 17 and second evaporator 18 open in the same direction. Therefore, it is easy to connect the ejector module 20 to the first evaporator 17 and the second evaporator 18.

Furthermore, since the ejector module 20 of the present embodiment functions as a joint part (connecting part) of the evaporator unit 200, it is possible to improve the assembling property to the ejector refrigeration cycle 10. Thereby, the productivity as the ejector-type refrigeration cycle 10 as a whole can be further improved.

(Second Embodiment)
In the present embodiment, an example in which the needle valve 53 and the nozzle-side drive mechanism 54 of the ejector 15 are abolished will be described as shown in FIGS. 6 and 7 with respect to the first embodiment.

That is, the nozzle portion 51 of the ejector 15 of the present embodiment is a fixed nozzle portion whose passage sectional area does not change. 6 and 7 correspond to FIGS. 2 and 5 described in the first embodiment, respectively. 6 and 7, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.

6 and 7, in the ejector module 20 of the present embodiment, the positional relationship between the ejector 15 and the variable aperture mechanism 16 is substantially the same as in the first embodiment. That is, the central axis CL of the nozzle portion 51 and the decompression side central axis CL2 are in a twisted positional relationship, and when viewed from the decompression side central axis CL2, the decompression side drive occupying the region indicated by the point hatching in FIG. The mechanism 62 and the central axis CL of the nozzle portion 51 are arranged so as to overlap. As shown in FIG. 7, the central axis CL of the nozzle portion 51 is positioned within the range of the vertical cross section of the pressure reducing side driving mechanism 62 and the pressure reducing side central axis CL2.

Other configurations and operations of the ejector module 20 and the ejector refrigeration cycle 10 are the same as those in the first embodiment. Therefore, the same effects as those of the first embodiment can be obtained also in the ejector refrigeration cycle 10 of the present embodiment.

More specifically, since the variable throttle mechanism 16 is connected to the other refrigerant outlet side of the branch portion 14, by adjusting the throttle opening of the variable throttle mechanism 16, the flow rate of the refrigerant flowing into the throttle passage 20a, And both the refrigerant | coolant flow rates which flow in into the nozzle part 51 can be adjusted. As a result, the ejector refrigeration cycle 10 can exhibit a high COP regardless of load fluctuations.

Further, in the ejector module 20 of the present embodiment, when the variable throttle mechanism 16 and the ejector 15 are integrated, the central axis of the decompression side drive mechanism 62 and the nozzle portion 51 when viewed from the decompression side central axis CL2 direction. It arrange | positions so that CL may superpose | polymerize.

According to such an arrangement, the decompression side drive mechanism 62 having a relatively large physique and the ejector 15 formed in a shape extending in the axial direction can be arranged while being shifted in the direction of the decompression side central axis CL2. Therefore, the main body (that is, the portion excluding the decompression side drive mechanism 62) of the variable aperture mechanism 16 and the ejector 15 can be disposed close to each other.

Further, since the central axis CL of the nozzle portion 51 and the pressure reducing side central axis CL2 are in a twisted positional relationship, the main body portion of the variable throttle mechanism 16 does not interfere with the pressure reducing side drive mechanism 62 and the ejector 15. And the ejector 15 can be brought close to each other effectively. Therefore, according to the ejector module 20 of the present embodiment, the applied ejector refrigeration cycle 10 is not enlarged even if the passage cross-sectional area is configured to be changeable.

Here, in the ejector module 20 of the present embodiment, the needle valve 53 and the nozzle-side drive mechanism 54 are abolished. Therefore, it is only necessary to adjust the passage sectional area of the throat portion of the nozzle portion 51 in advance. It is difficult to appropriately adjust the degree of superheat of the outlet side refrigerant of the one evaporator 17.

Therefore, in the ejector refrigeration cycle 10 of the present embodiment, the gas-phase refrigerant separated by separating the gas-liquid of the low-pressure refrigerant between the low-pressure outlet 21f of the ejector module 20 and the suction port of the compressor 11 is used as the compressor. You may arrange | position the accumulator which flows out into the 11 inlets.

(Third embodiment)
In the present embodiment, as shown in FIG. 8, an electric nozzle-side drive mechanism 541 having an actuator such as a stepping motor is employed as the nozzle-side drive unit as compared with the first embodiment. The operation of the nozzle side drive mechanism 541 is controlled by a control signal (control pulse) output from the air conditioning control device. FIG. 8 is a drawing corresponding to FIG. 2 described in the first embodiment.

Further, in the ejector module 20 of the present embodiment, the nozzle-side central axis CL1 and the pressure-reducing side central axis CL2 have a twisted positional relationship, as in the first embodiment, and the nozzle-side central axis CL1 and the pressure-reducing side central axis When viewed from the direction of one central axis of CL2, the drive unit corresponding to one central axis and the other central axis are superposed.

Other configurations and operations of the ejector module 20 are the same as those in the first embodiment. Therefore, even if the type of the nozzle side drive unit is changed as in the ejector module 20 of the present embodiment, the same effect as that of the first embodiment can be obtained.

(Fourth embodiment)
In the present embodiment, as shown in FIG. 9, an electric pressure-reducing side driving mechanism 621 having an actuator such as a stepping motor is employed as the pressure-reducing side driving unit as compared with the first embodiment. The operation of the decompression side drive mechanism 621 is controlled by a control signal (control pulse) output from the air conditioning control device. FIG. 9 is a drawing corresponding to FIG. 3 described in the first embodiment.

Other configurations and operations of the ejector module 20 are the same as those in the first embodiment. Therefore, even if the type of the decompression side drive unit is changed as in the ejector module 20 of the present embodiment, the same effect as that of the first embodiment can be obtained.

(Fifth embodiment)
In the present embodiment, as shown in FIG. 10, the ejector side outlet 21c is opened in the same direction as the low pressure inlet 21e, the refrigerant suction port 21b, and the throttle side outlet 21d as compared with the first embodiment, and the body portion 21 is opened on the same plane of the outer surface.

Other configurations and operations of the ejector module 20 are the same as those in the first embodiment. Therefore, also in the ejector module 20 of this embodiment, the effect similar to 1st Embodiment can be acquired. Further, as shown in the present embodiment, the ejector side outlet 21c is arranged in the same plane as the other refrigerant inlets / outlets 21b to 21d, so that the assembling property of the ejector refrigeration cycle 10 can be improved.

(Sixth embodiment)
In the present embodiment, an example in which the evaporator unit 200 using the ejector module 20 described in the fourth embodiment is applied to the ejector refrigeration cycle 10a illustrated in the overall configuration diagram of FIG. 11 will be described.

The ejector-type refrigeration cycle 10a is applied to the vehicle air conditioner 1, and functions to cool or heat the air blown into the passenger compartment that is the air-conditioning target space. The ejector refrigeration cycle 10a is configured to be capable of switching between a cooling mode refrigerant circuit, a dehumidifying heating mode refrigerant circuit, and a heating mode refrigerant circuit.

In the vehicle air conditioner 1, the cooling mode is an operation mode in which cooling of the vehicle interior is performed by blowing out the cooled blown air into the vehicle interior. The heating mode is an operation mode in which the vehicle interior is heated by blowing heated air into the vehicle interior. The dehumidifying heating mode is an operation mode in which dehumidifying heating in the vehicle interior is performed by reheating the blown air that has been cooled and dehumidified and blowing it out into the vehicle interior.

In addition, in FIG. 11, the flow of the refrigerant | coolant in the refrigerant circuit of the air_conditioning | cooling mode is shown with the white arrow. The flow of the refrigerant in the refrigerant circuit in the heating mode is indicated by black arrows. The flow of the refrigerant in the refrigerant circuit in the dehumidifying and heating mode is indicated by hatched arrows.

In the ejector refrigeration cycle 10a, the radiator 12 having only the condensing part described in the first embodiment is employed. Furthermore, in this embodiment, the heat radiator 12 is arrange | positioned in the casing 31 of the indoor air conditioning unit 30 mentioned later. Therefore, the radiator 12 of this embodiment can be expressed as an indoor condenser.

The refrigerant outlet of the radiator 12 is connected to the inlet side of the first three-way joint 22a having three inlets and outlets communicating with each other. As such a three-way joint, one formed by joining a plurality of pipes or one formed by providing a plurality of refrigerant passages in a metal block or a resin block can be adopted.

The three-way joint functions as a branching portion that branches the refrigerant flow by using one of the three inlets and outlets as an inlet and the remaining two as outlets. In addition, the three-way joint functions as a merging portion that merges the two refrigerant flows by using two of the three inflow / outflow ports as inflow ports and the remaining one as the outflow port.

Furthermore, as will be described later, the ejector refrigeration cycle 10a includes second to fourth three-way joints 22b to 22d. The basic configuration of the second to fourth three-way joints 22b to 22d is the same as that of the first three-way joint 22a.

One inlet of the second three-way joint 22b is connected to one outlet of the first three-way joint 22a via a heating expansion valve 23. The other inflow side of the second three-way joint 22b is connected to the other outflow port of the first three-way joint 22a via the first on-off valve 24a. The refrigerant inlet side of the outdoor heat exchanger 25 is connected to the outlet of the second three-way joint 22b.

The heating expansion valve 23 is a decompression device that decompresses the high-pressure refrigerant that has flowed out of the radiator 12 at least in the heating mode. The heating expansion valve 23 is an electric variable throttle mechanism that includes a valve body that can change the throttle opening and an electric actuator that changes the opening of the valve body. The operation of the heating expansion valve 23 is controlled by a control signal (control pulse) output from the air conditioning control device.

The first on-off valve 24a is an electromagnetic valve that opens and closes a bypass passage that connects the other outlet of the first three-way joint 22a and the other inlet of the second three-way joint 22b. Further, the ejector refrigeration cycle 10a includes a second on-off valve 24b as will be described later. The basic configuration of the second on-off valve 24b is the same as that of the first three-way joint 22a. The operations of the first and second on-off

valves

24a and 24b are controlled by a control voltage output from the air conditioning control device.

Here, the pressure loss that occurs when the refrigerant passes through the first on-off valve 24a is extremely small compared to the pressure loss that occurs when the refrigerant passes through the heating expansion valve 23. Therefore, when the first on-off valve 24a is open, the refrigerant that has flowed from the radiator 12 into the first three-way joint 22a hardly flows out to the heating expansion valve 23 side, but flows out to the first on-off valve 24a side. To do.

The outdoor heat exchanger 25 is a heat exchanger for exchanging heat between the refrigerant flowing out of the heating expansion valve 23 and the outside air blown from the outside air fan 25a. The outdoor heat exchanger 25 is disposed on the front side in the vehicle bonnet.

The outdoor heat exchanger 25 functions as a radiator that radiates high-pressure refrigerant at least in the cooling mode, and functions as an evaporator that evaporates low-pressure refrigerant decompressed by the heating expansion valve 23 at least in the heating mode. The outside air fan 25a is an electric blower in which the rotation speed (that is, the blowing capacity) is controlled by a control voltage output from the air conditioning control device.

The inlet of the third three-way joint 22c is connected to the refrigerant outlet of the outdoor heat exchanger 25. The refrigerant inlet side of the evaporator unit 200 (that is, the high pressure inlet 21a side of the ejector module 20) is connected to one outlet of the third three-way joint 22c. One inlet of the fourth three-way joint 22d is connected to the refrigerant outlet of the evaporator unit 200 (that is, the low pressure outlet 21f of the ejector module 20).

The other inflow port of the fourth three-way joint 22d is connected to the other outflow port of the third three-way joint 22c through the second on-off valve 24b. The inlet side of the accumulator 26 is connected to the outlet of the fourth three-way joint 22d. The accumulator 26 is a gas-liquid separator that separates the gas-liquid of the refrigerant that has flowed into the accumulator and stores excess liquid-phase refrigerant in the cycle. The suction port side of the compressor 11 is connected to the gas phase refrigerant outlet of the accumulator 26.

Further, in the ejector module 20 of the present embodiment, as shown in FIG. 12, the maximum passage cross-sectional area A1 when the decompression side drive mechanism 621 displaces the throttle valve 61 to fully open the throttle passage 20a is the high pressure inlet 21a. Is set to be equal to or larger than the minimum passage cross-sectional area A2 (A1 ≧ A2) of the refrigerant passage (in other words, the refrigerant passage on the upstream side of the restriction passage 20a) from the throttle passage 20a. FIG. 12 is a drawing corresponding to FIG. 9 described in the fourth embodiment.

For this reason, the pressure loss that occurs when the refrigerant passes through the throttle passage 20a that is fully open is extremely small compared to the pressure loss that occurs when the refrigerant passes through the nozzle portion 51 of the ejector module 20. Accordingly, when the throttle passage 20a is fully open, the refrigerant that has flowed into the high pressure inlet 21a of the ejector module 20 hardly flows out from the branch portion 14 to the nozzle portion 51 side, and almost the entire flow rate is from the branch portion 14. It flows out to the throttle passage 20a side.

Other configurations of the ejector refrigeration cycle 10a are the same as those of the ejector refrigeration cycle 10 of the first embodiment.

Next, the indoor air conditioning unit 30 will be described. The indoor air conditioning unit 30 is disposed inside the instrument panel (instrument panel) at the forefront of the vehicle interior. The indoor air conditioning unit 30 is for blowing out the blown air whose temperature has been adjusted by the ejector refrigeration cycle 10a to an appropriate location in the passenger compartment.

As shown in FIG. 11, the indoor air conditioning unit 30 includes a blower 18 a, an evaporator unit 200, a radiator 12, and the like in an air passage formed inside a casing 31 that forms an outer shell thereof.

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

The inside / outside air switching device 33 continuously adjusts the opening area of the inside air introduction port for introducing the inside air into the casing 31 and the outside air introduction port for introducing the outside air, by the inside / outside air switching door, The introduction ratio with the introduction air volume is 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.

A blower 18 a is arranged on the downstream side of the blown air flow of the inside / outside air switching device 33. Furthermore, the evaporator unit 200 and the radiator 12 are arranged in this order with respect to the flow of the blown air on the downstream side of the blower air flow of the blower 18a. That is, the evaporator unit 200 is arranged on the upstream side of the blower air flow with respect to the radiator 12.

Further, in the casing 31, a cold air bypass passage 35 is formed in which the blown air that has passed through the evaporator unit 200 is caused to bypass the radiator 12 and flow downstream.

On the downstream side of the blower air flow of the evaporator unit 200 and on the upstream side of the blower air flow of the radiator 12, of the blown air that has passed through the evaporator unit 200, the amount of air passing through the radiator 12 and the cold air bypass An air mix door 34 that adjusts the air volume ratio with the air volume that passes through the passage 35 is disposed.

On the downstream side of the blast air flow of the radiator 12, a mixing space for mixing the blast air heated by the radiator 12 and the blast air that has passed through the cold air bypass passage 35 and is not heated by the radiator 12 is provided. It has been. Furthermore, the opening hole which blows off the blowing air (air-conditioning wind) mixed in the mixing space in the vehicle interior at the most downstream part of the blowing air flow of the casing 31 is arranged.

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 temperature of the conditioned air mixed in the mixing space is adjusted by the air mix door 34 adjusting the air volume ratio between the air volume passing through the radiator 12 and the air volume passing through the cold air bypass passage 35. Thereby, the temperature of the blast air (air conditioned air) blown out from each outlet into the vehicle compartment is also adjusted.

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.

Further, on the upstream side of the air flow of the face opening hole, foot opening hole, and defroster opening hole, a face door for adjusting the opening area of the face opening hole, a foot door for adjusting the opening area of the foot opening hole, and a defroster opening, respectively. A defroster door (both not shown) for adjusting the opening area of the hole is disposed.

These face doors, foot doors, and defroster doors constitute an air outlet mode switching device that switches an air outlet from which air-conditioned air is blown. The face door, the foot door, and the defroster door are connected to an electric actuator for driving the air outlet mode door via a link mechanism and the like, and are rotated in conjunction with each other. The operation of the electric actuator is controlled by a control signal output from the air conditioning control device.

Next, the operation of this embodiment in the above configuration will be described. In the vehicle air conditioner 1 of the present embodiment, cooling, heating, and dehumidifying heating can be performed in the passenger compartment. Accordingly, in the ejector refrigeration cycle 10a, the operation in the cooling mode, the heating mode, and the dehumidifying heating mode can be switched. Switching between these operation modes is performed by executing an air conditioning control program stored in the air conditioning control device.

In this air conditioning control program, the refrigerant circuit is switched based on the target blowing temperature TAO and the outside air temperature Tam of the blown air blown into the vehicle interior. More specifically, the heating mode → the dehumidifying heating mode → the cooling mode is switched in this order as the target blowing temperature TAO or the outside air temperature Tam increases. Below, the operation | movement of each operation mode is demonstrated.

(A) Cooling mode In the cooling mode, the air conditioning control device fully closes the heating expansion valve 23, opens the first on-off valve 24a, closes the second on-off valve 24b, and in the throttle passage 20a of the ejector module 20. The operation of the decompression side drive mechanism 621 is controlled so that the refrigerant decompression action is exhibited.

Thereby, in the ejector refrigeration cycle 10a in the cooling mode, as indicated by the white arrow in FIG. 11, the compressor 11 (→ the radiator 12) → the first on-off valve 24a → the outdoor heat exchanger 25 → the evaporator unit 200 A refrigeration cycle in which refrigerant circulates in the order of accumulator 26 → compressor 11 is configured.

With this cycle configuration, the air conditioning control device refers to the control map stored in advance in the air conditioning control device based on the target blowing temperature TAO, and the target evaporator temperature TEO of the blown air blown from the evaporator unit 200. To decide. Then, the operation of the compressor 11 is controlled so that the evaporator temperature of the first evaporator 17 of the evaporator unit 200 approaches the target evaporator temperature TEO.

In this control map, the target evaporator temperature TEO is determined to decrease as the target blowout temperature TAO decreases. Further, the target evaporator temperature TEO is determined to be a value within a range (specifically, 1 ° C. or higher) in which frost formation of the first evaporator 17 and the second evaporator 18 can be suppressed.

In addition, the air conditioning control device displaces the air mix door 34 so that the air passage on the radiator 12 side is fully closed and the cold air bypass passage 35 side is fully opened.

Therefore, in the cooling mode, the high-pressure refrigerant discharged from the compressor 11 flows into the radiator 12. In the cooling mode, since the air mix door 34 fully closes the ventilation path on the radiator 12 side, the high-pressure refrigerant flowing into the radiator 12 flows out of the radiator 12 without radiating heat to the blown air. The high-pressure refrigerant that has flowed out of the radiator 12 flows into the outdoor heat exchanger 25 through the first on-off valve 24a.

The high-pressure refrigerant that has flowed into the outdoor heat exchanger 25 exchanges heat with the outside air blown by the outside air fan 25a, dissipates heat, and condenses. The refrigerant condensed in the outdoor heat exchanger 25 flows into the evaporator unit 200 (specifically, the high pressure inlet 21a of the ejector module 20). The refrigerant flowing into the ejector module 20 absorbs heat from the blown air and evaporates in the first evaporator 17 and the second evaporator 18 as in the first embodiment.

The refrigerant that has flowed out of the evaporator unit 200 (specifically, the low-pressure outlet 21f of the ejector module 20) flows into the accumulator 26. The gas-phase refrigerant separated by the accumulator 26 is sucked into the compressor 11.

That is, in the ejector refrigeration cycle 10a in the cooling mode, a refrigeration cycle is configured in which the outdoor heat exchanger 25 functions as a radiator and the first evaporator 17 and the second evaporator 18 of the evaporator unit 200 function as an evaporator. Is done. Therefore, in the cooling mode, the vehicle interior can be cooled by blowing the blown air cooled by the first evaporator 17 and the second evaporator 18 of the evaporator unit 200 into the vehicle interior.

(B) Heating mode In the heating mode, the air-conditioning control device sets the heating expansion valve 23 to a throttled state that exerts a refrigerant decompression action, closes the first on-off valve 24a, opens the second on-off valve 24b, and sets the ejector module 20 The operation of the decompression side drive mechanism 621 is controlled so as to close the throttle passage 20a.

As a result, in the ejector refrigeration cycle 10a in the heating mode, as indicated by the black arrows in FIG. 11, the compressor 11, the radiator 12, the heating expansion valve 23, the outdoor heat exchanger 25, the second on-off valve 24b, A refrigeration cycle in which the refrigerant circulates in the order of accumulator 26 → compressor 11 is configured.

With this cycle configuration, the air conditioning control device determines the target condenser pressure PCO of the high-pressure refrigerant flowing into the radiator 12 with reference to the control map stored in the air conditioning control device in advance based on the target outlet temperature TAO. To do. Then, the operation of the compressor 11 is controlled so that the pressure of the high-pressure refrigerant flowing into the radiator 12 approaches the target condenser pressure PCO.

In this control map, the target condenser pressure PCO is determined to increase as the target outlet temperature TAO increases.

Also, the air conditioning control device displaces the air mix door 34 so that the ventilation path on the radiator 12 side is fully opened and the cold air bypass path 35 side is fully closed.

Therefore, in the heating mode, the high-pressure refrigerant discharged from the compressor 11 flows into the radiator 12. In the heating mode, since the air mix door 34 fully opens the ventilation path on the radiator 12 side, the high-pressure refrigerant flowing into the radiator 12 radiates heat by exchanging heat with the blown air. The refrigerant flowing out of the radiator 12 flows into the heating expansion valve 23 and is decompressed. The low-pressure refrigerant decompressed by the heating expansion valve 23 flows into the outdoor heat exchanger 25.

The low-pressure refrigerant that has flowed into the outdoor heat exchanger 25 absorbs heat from the outside air blown by the outside air fan 25a and evaporates. Since the second on-off valve 24b is opened, the refrigerant evaporated in the outdoor heat exchanger 25 hardly flows into the evaporator unit 200 side (specifically, the ejector module 20 side), and the second on-off valve It flows into the accumulator 26 through 24b. The gas-phase refrigerant separated by the accumulator 26 is sucked into the compressor 11.

That is, in the ejector refrigeration cycle 10a in the heating mode, a refrigeration cycle is configured in which the radiator 12 functions as a radiator and the outdoor heat exchanger 25 functions as an evaporator. Therefore, in the heating mode, the vehicle interior can be heated by blowing the blown air heated by the radiator 12 into the vehicle interior.

(C) Dehumidifying Heating Mode In the dehumidifying heating mode, the air conditioning control device places the heating expansion valve 23 in the throttle state, closes the first on-off valve 24a, closes the second on-off valve 24b, and opens the throttle passage 20a of the ejector module 20. The operation of the decompression side drive mechanism 621 is controlled so as to be fully opened.

Thus, in the ejector refrigeration cycle 10a in the dehumidifying heating mode, as indicated by the hatched arrows in FIG. 11, the compressor 11 → the radiator 12 → the heating expansion valve 23 → the outdoor heat exchanger 25 → the evaporator unit 200 A refrigeration cycle in which refrigerant circulates in the order of accumulator 26 → compressor 11 is configured.

In this cycle configuration, the air conditioning control device controls the operation of the compressor 11 as in the cooling mode. For this reason, also in dehumidification heating mode, the refrigerant | coolant evaporation temperature in the 1st evaporator 17 and the 2nd evaporator 18 is set to 1 degreeC or more.

Therefore, in the dehumidifying heating mode, the high-pressure refrigerant discharged from the compressor 11 flows into the radiator 12. In the dehumidifying and heating mode, since the air mix door 34 fully opens the ventilation path on the radiator 12 side, the high-pressure refrigerant flowing into the radiator 12 radiates heat by exchanging heat with the blown air. The refrigerant flowing out of the radiator 12 flows into the heating expansion valve 23 and is decompressed. The low-pressure refrigerant decompressed by the heating expansion valve 23 flows into the outdoor heat exchanger 25.

The low-pressure refrigerant that has flowed into the outdoor heat exchanger 25 absorbs heat from the outside air blown by the outside air fan 25a and evaporates. The refrigerant evaporated in the outdoor heat exchanger 25 flows into the evaporator unit 200 (specifically, the high pressure inlet 21a of the ejector module 20) because the second on-off valve 24b is closed.

The refrigerant that has flowed into the evaporator unit 200 flows into the throttle passage 20a side with almost no flow into the nozzle portion 51 side because the throttle passage 20a is fully open. Then, the refrigerant flows in the order of the first evaporator 17 → the refrigerant suction port 21 b of the ejector 15 → the diffuser portion 52 of the ejector 15 → the second evaporator 18. At this time, the refrigerant absorbs heat from the blown air in the first evaporator 17 and the second evaporator 18 and further evaporates.

That is, in the ejector type refrigeration cycle 10a in the dehumidifying and heating mode, a refrigeration cycle in which the radiator 12 functions as a radiator and the outdoor heat exchanger 25, the first evaporator 17, and the second evaporator 18 function as an evaporator is configured. Is done. Therefore, in the dehumidifying heating mode, the blown air cooled and dehumidified by the first evaporator 17 and the second evaporator 18 of the evaporator unit 200 is reheated by the radiator 12 and blown out into the passenger compartment. Dehumidification heating in the passenger compartment can be performed.

Here, in the dehumidifying heating mode, the heat that the refrigerant has absorbed from the outside air in the outdoor heat exchanger 25 and the heat that the refrigerant has absorbed from the blown air in the first evaporator 17 and the second evaporator 18 are used as heat sources. Blowing air is reheated. Therefore, in order to improve the heating capability of the blown air in the dehumidifying heating mode, it is necessary to increase the heat absorption amount of the refrigerant in the outdoor heat exchanger 25, the first evaporator 17, and the second evaporator 18.

Furthermore, in the dehumidifying and heating mode, the outdoor heat exchanger 25, the first evaporator 17, and the second evaporator 18 form a refrigerant circuit connected in series in this order with respect to the refrigerant flow. For this reason, the refrigerant evaporation temperature in the outdoor heat exchanger 25 cannot be made lower than the refrigerant evaporation temperatures of the first evaporator 17 and the second evaporator 18.

Therefore, in the ejector-type refrigeration cycle 10a, in order to improve the heating capability in the dehumidifying heating mode, the refrigerant evaporation temperatures of the first evaporator 17 and the second evaporator 18 are lowered within a range in which frost formation can be suppressed. Furthermore, it is effective to make the refrigerant evaporation temperature in the outdoor heat exchanger 25 close to the refrigerant evaporation temperature of the first evaporator 17 and the second evaporator 18.

Therefore, in the ejector module 20 of the present embodiment, the maximum passage sectional area A1 when the throttle passage 20a is fully opened is set to be equal to or larger than the minimum passage sectional area A2 of the refrigerant passage on the upstream side of the throttle passage 20a.

According to this, it is possible to suppress an increase in pressure loss that occurs when the refrigerant passes through the throttle passage 20a that is fully open. Therefore, the refrigerant evaporation temperature in the outdoor heat exchanger 25 can be brought close to the refrigerant evaporation temperatures of the first evaporator 17 and the second evaporator 18. As a result, it is possible to suppress a decrease in the heat absorption amount in the outdoor heat exchanger 25, and it is possible to suppress a decrease in the heating capacity when reheating the blown air.

As described above, according to the ejector module 20 of the present embodiment, the ejector that is switched to the refrigerant circuit in which the outdoor heat exchanger 25, the first evaporator 17, and the second evaporator 18 are connected in series to the refrigerant flow. It becomes possible to apply to a type refrigeration cycle. This is effective in that the range of the ejector refrigeration cycle to which the ejector module 20 can be applied can be expanded.

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

(1) In each of the above-described embodiments, the example in which the ejector module 20 according to the present disclosure is applied to the ejector refrigeration cycle 10 mounted on a vehicle has been described, but the application of the ejector module 20 is not limited thereto. For example, the present invention may be applied to an ejector-type refrigeration cycle used in a stationary air conditioner, a cold / hot storage, or the like.

(2) In the first embodiment described above, the ejector module 20 including the variable aperture mechanism 16 and the ejector 15 having the variable nozzle portion has been described. However, the ejector module 20 is not limited to this. In order to bring the flow rate of the refrigerant flowing into the throttle passage 20a and the nozzle portion 51 close to an appropriate flow rate in accordance with the load fluctuation of the ejector refrigeration cycle 10, at least one passage sectional area of the throttle passage 20a and the nozzle portion 51 is used. Should just be configured to be changeable.

Therefore, as described in the second embodiment, the variable throttle mechanism 16 may be employed, and the ejector 15 having the fixed nozzle portion may be employed. Furthermore, the throttle valve 61 and the pressure reducing side drive mechanism 62 may be eliminated from the first embodiment. That is, instead of the variable aperture mechanism 16, a fixed aperture may be employed, and an ejector 15 having a variable nozzle portion may be employed.

In the first embodiment, the nozzle side temperature sensing portion 54a is disposed in the space communicating with the outflow side passage 20c. However, at least a part of the nozzle side temperature sensing portion 54a is disposed in the outflow side passage 20c. May be. Furthermore, although an example in which a part of the decompression side drive mechanism 62 is disposed in the suction side passage 20b has been described, the decompression side drive mechanism 62 may be disposed in a space communicating with the suction side passage 20b.

In the first embodiment, an example in which at least a part of the diffuser unit 52 is accommodated in the collective pipe 19 has been described. However, at least a part of the diffuser unit 52 is disposed in the second evaporator 18 (for example, collective distribution). May be accommodated in a tank for use.

(3) Each component device constituting the

ejector refrigeration cycle

10, 10a 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 employed as the compressor 11 has been described. However, the compressor 11 is driven by a rotational driving force transmitted from a vehicle traveling engine via a pulley, a belt, or the like. An engine driven compressor may be employed. Furthermore, as an engine-driven compressor, the variable capacity compressor that can adjust the refrigerant discharge capacity by changing the discharge capacity, or the refrigerant discharge capacity can be adjusted by changing the operating rate of the compressor by intermittently connecting the electromagnetic clutch A fixed-capacity compressor can be employed.

In the first to fifth embodiments described above, an example in which a receiver-integrated condenser is employed as the radiator 12 has been described. Further, supercooling that supercools the liquid-phase refrigerant that has flowed out of the receiver unit 12b is described. You may employ | adopt what is called a subcool type | mold condenser comprised with a part. In addition, as described in the sixth embodiment, the radiator 12 including only the condensing unit may be employed.

In the above-described embodiment, the example in which the first evaporator 17 and the second evaporator 18 are configured integrally has been described. However, the first evaporator 17 and the second evaporator 18 may be configured separately. Good. In the first evaporator 17 and the second evaporator 18, different refrigerant target fluids may be cooled in different temperature zones.

Further, in the sixth embodiment described above, an example in which the heating expansion valve 23 and the first on-off valve 24a are employed has been described. However, as the heating expansion valve 23, the refrigerant decompression action is achieved by fully opening the valve opening degree. You may employ | adopt the thing which has the full open function which functions as a mere refrigerant path almost without exhibiting, and the fully closed function which obstruct | occludes a refrigerant path by making a valve opening degree full close. According to this, the 1st on-off valve 24a, the 1st, 2nd three-way joint 22a, 22b can be abolished.

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. Furthermore, a supercritical refrigeration cycle in which carbon dioxide is employed as the refrigerant and the high-pressure side refrigerant pressure is equal to or higher than the critical pressure of the refrigerant may be configured.

(4) In the above-described sixth embodiment, the example in which the operation of the decompression side drive mechanism 621 is controlled so that the throttle passage 20a of the ejector module 20 is fully opened in the dehumidifying heating mode has been described. The operation of is not limited to this. For example, the operation of the decompression side drive mechanism 621 may be controlled so that the throttle passage 20a is in a throttled state under operating conditions that can sufficiently ensure the heating capacity of the blower air in the radiator 12.

(5) Further, the means and components disclosed in each of the above embodiments may be appropriately combined within a practicable range. For example, in the ejector module 20 of the first and fifth embodiments, the nozzle side driving mechanism 541 described in the third embodiment and the pressure reducing side driving mechanism 621 described in the fourth embodiment may be simultaneously employed. In other words, the ejector module 20 having the electric variable aperture mechanism 16 and the electric variable nozzle portion may be used.

In the sixth embodiment, the example in which the evaporator unit 200 using the ejector module 20 described in the fourth embodiment is applied to the ejector refrigeration cycle 10a has been described. Of course, the first to third embodiments are described. The evaporator unit 200 using the ejector module 20 described in the above may be applied. In this case, when a refrigerant having a relatively high dryness (for example, a dryness of 0.5 or more) flows into the high-pressure inlet 21a of the ejector module 20, the decompression-side drive mechanism 62 is set so that the throttle passage 20a is fully opened. Adjust the operation.

Claims

The compressor (11) that compresses and discharges the refrigerant, the radiator (12) that dissipates the refrigerant discharged from the compressor, the first evaporator (17) that evaporates the refrigerant, and the compressor that evaporates the refrigerant An ejector module applied to an ejector refrigeration cycle (10) having a second evaporator (18) that flows out to the suction side of the machine,
A nozzle part (51) for depressurizing and injecting a part of the refrigerant flowing out of the radiator;
A decompression section (20a) for decompressing another part of the refrigerant flowing out of the radiator;
A body part (21) formed with a refrigerant suction port (21b) for sucking the refrigerant from the outside by the suction action of the jetted refrigerant jetted from the nozzle part;
A pressure increasing unit (52) for increasing the pressure of the mixed refrigerant of the jet refrigerant and the suction refrigerant sucked from the refrigerant suction port;
A pressure reducing side valve body portion (61) for changing a passage sectional area of the pressure reducing portion;
A pressure reducing side driving part (62, 621) for displacing the pressure reducing side valve body part,
A refrigerant inlet side of the first evaporator is connected to the throttle side outlet (21d) for allowing the refrigerant to flow out from the decompression unit,
A refrigerant outlet side of the first evaporator is connected to the refrigerant suction port;
A refrigerant inlet side of the second evaporator is connected to an ejector side outlet (21c) for allowing the refrigerant to flow out from the pressure increasing unit,
A central axis in a displacement direction in which the decompression side drive unit displaces the decompression side valve body is defined as a decompression side center axis (CL2), and when viewed from the decompression side center axis (CL2) direction, the decompression side An ejector module in which the drive unit and the central axis (CL) of the nozzle unit are arranged in an overlapping manner.
The ejector module according to claim 1, wherein the decompression side central axis (CL2) and the central axis (CL) of the nozzle portion are in a torsional positional relationship.
The compressor (11) that compresses and discharges the refrigerant, the radiator (12) that dissipates the refrigerant discharged from the compressor, the first evaporator (17) that evaporates the refrigerant, and the compressor that evaporates the refrigerant An ejector module applied to an ejector-type refrigeration cycle (10) having a second evaporator (18) that flows out to the suction side of
A nozzle part (51) for depressurizing and injecting a part of the refrigerant flowing out of the radiator;
A decompression section (20a) for decompressing another part of the refrigerant flowing out of the radiator;
A body part (21) formed with a refrigerant suction port (21b) for sucking the refrigerant from the outside by the suction action of the jetted refrigerant jetted from the nozzle part;
A pressure increasing unit (52) for increasing the pressure of the mixed refrigerant of the jet refrigerant and the suction refrigerant sucked from the refrigerant suction port;
A nozzle side valve body portion (53) for changing a passage cross-sectional area of the nozzle portion;
A nozzle side drive section (54, 541) for displacing the nozzle side valve body section;
A pressure reducing side valve body portion (61) for changing a passage sectional area of the pressure reducing portion;
A pressure reducing side driving part (62, 621) for displacing the pressure reducing side valve body part,
A refrigerant inlet side of the first evaporator is connected to the throttle side outlet (21d) for allowing the refrigerant to flow out from the decompression unit,
A refrigerant outlet side of the first evaporator is connected to the refrigerant suction port;
A refrigerant inlet side of the second evaporator is connected to an ejector side outlet (21c) for allowing the refrigerant to flow out from the pressure increasing unit,
A central axis in a displacement direction in which the nozzle side drive unit displaces the nozzle side valve body portion is defined as a nozzle side central axis (CL1), and the pressure reduction side drive unit in a displacement direction in which the pressure reduction side valve body portion is displaced. Define the central axis as the decompression side central axis (CL2),
When viewed from the direction of one central axis of the nozzle side central axis (CL1) and the decompression side central axis (CL2), the driving unit corresponding to the one central axis and the other central axis are arranged in an overlapping manner. Ejector module.
The ejector module according to claim 3, wherein the nozzle side central axis (CL1) and the pressure reducing side central axis (CL2) are in a torsional positional relationship.
The body part is formed with an outflow side passage (20c) through which the refrigerant that has flowed out of the second evaporator flows.
The nozzle side drive unit includes a nozzle side temperature sensing part (54a) having a nozzle side deformation member (54b) that deforms according to the temperature and pressure of the refrigerant flowing out of the second evaporator,
5. The ejector module according to claim 3, wherein at least a part of the nozzle side temperature sensing unit is disposed in the outflow side passage or in a space communicating with the outflow side passage.
The body part is formed with a suction side passage (20b) for circulating the refrigerant flowing out of the first evaporator,
The decompression side drive unit (62) includes a decompression side temperature sensing unit (62a) having a decompression side deformation member (62b) that deforms according to the temperature and pressure of the refrigerant flowing out of the first evaporator,
6. The ejector module according to claim 1, wherein at least a part of the decompression-side temperature sensing unit is disposed in the suction-side passage or in a space communicating with the suction-side passage.
7. The pressure reduction side drive unit is configured to displace the pressure reduction side valve body so that the degree of superheat of the outlet side refrigerant of the first evaporator approaches 0 ° C. 7. The ejector module described.
At least a part of the boosting part protrudes from the body part so that it can be accommodated in the second evaporator or in the pipe (19) connected to the second evaporator. The ejector module according to claim 1.
The body portion has a high-pressure inlet (21a) through which the refrigerant flowing out from the radiator flows in, an outflow side passage (20c) for guiding the refrigerant flowing out from the second evaporator to the suction port side of the compressor, and the outflow A low-pressure inlet (21e) for allowing the refrigerant to flow into the side passage, and a low-pressure outlet (21f) for letting the refrigerant flow out of the outflow-side passage,
The high pressure inlet and the low pressure outlet are open in the same direction,
The ejector module according to claim 1, wherein the ejector side outlet, the low pressure inlet, the refrigerant suction port, and the throttle side outlet are open in the same direction.
The body portion is formed with a high-pressure inlet (21a) through which the refrigerant flowing out of the radiator flows.
The maximum passage sectional area (A1) of the decompression unit when the decompression side drive unit displaces the decompression side valve body part is the minimum passage sectional area (A2) of the refrigerant passage from the high pressure inlet to the decompression unit. The ejector module according to any one of claims 1 to 9, which is configured as described above.