WO2018159320A1

WO2018159320A1 - Ejector module

Info

Publication number: WO2018159320A1
Application number: PCT/JP2018/005439
Authority: WO
Inventors: 照之堀田; 達博鈴木; 尾形　豪太; 陽一郎河本; 龍福島
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
Also published as: JP2018146141A; JP6717234B2

Abstract

An ejector module applied to a steam-compression-type refrigeration cycle device is provided with a nozzle unit (15a) for decompressing a refrigerant and ejecting the refrigerant, a decompression unit (20a) for decompressing the refrigerant, a body part (21) provided with a pressure-raising unit (15c) and a refrigerant inlet (21b) of an ejector, a valve body part (22) for changing both the channel cross-section area of the nozzle unit and the channel cross-section area of the decompression unit, and a driving mechanism unit (23) for displacing the valve body part. The driving mechanism unit is configured from a mechanical mechanism having a deformation member (23b) that deforms in response to a change in the pressure and/or the temperature of the refrigerant.

Description

Ejector module

Cross-reference of related applications

This application is based on Japanese Patent Application No. 2017-039253 filed on Mar. 2, 2017, the disclosure of which is incorporated herein by reference.

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

According to the study of the inventors of the present disclosure, the evaporator unit of Patent Document 1 employs a fixed throttle, and further employs a fixed nozzle portion whose passage cross-sectional area cannot be changed 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 described that a variable nozzle portion configured to be able to change the passage cross-sectional area of the refrigerant passage in the nozzle portion may be adopted.

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 applied to a vapor compression refrigeration cycle apparatus according to a feature example of the present disclosure includes a nozzle unit that decompresses and injects a refrigerant, a decompression unit that decompresses the refrigerant, and an injection injected from the nozzle unit A body part formed with a refrigerant suction port for sucking the refrigerant from outside by a suction action of the refrigerant, and a pressure increasing unit for boosting the mixed refrigerant of the injected refrigerant and the suction refrigerant sucked from the refrigerant suction port; A valve body section that changes both the area and the passage cross-sectional area of the decompression section; and a drive mechanism section that displaces the valve body section. Furthermore, the drive mechanism part is comprised with the mechanical mechanism which has a deformation member which deform | transforms according to the change of at least one of the temperature and pressure of a refrigerant | coolant.

Since the ejector module includes a nozzle part, a body part, a valve body part, and a drive mechanism part, an ejector having a variable nozzle part can be configured. Furthermore, since the ejector module includes a decompression section, a valve body section, and a drive mechanism section, a variable throttle mechanism can be configured.

Therefore, according to the load fluctuation of the applied ejector type refrigeration cycle, the valve body portion can be displaced, and the passage sectional area of the nozzle portion and the throttle opening of the variable throttle mechanism can be changed in conjunction with each other. As a result, a high COP can be exhibited in the ejector refrigeration cycle regardless of load fluctuations.

Furthermore, since the passage cross-sectional area of the nozzle part and the throttle opening of the pressure reducing part are adjusted by one common driving mechanism part and valve body part, it does not cause an increase in size compared to those equipped with a plurality of driving mechanisms. In addition, the ejector having the variable nozzle portion and the variable aperture mechanism can be integrated.

In addition to this, since the drive mechanism portion is composed of a mechanical mechanism, there is no need for electrical connection to displace the valve body portion.

Therefore, it is possible 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 applied to a vapor compression refrigeration cycle apparatus according to another characteristic example of the present disclosure is injected from a nozzle unit that decompresses and injects a refrigerant, a decompression unit that decompresses the refrigerant, and the nozzle unit. A body part formed with a refrigerant suction port for sucking the refrigerant from the outside by the suction action of the injected refrigerant, and a pressure increasing unit for boosting the mixed refrigerant of the injected refrigerant and the suction refrigerant sucked from the refrigerant suction port, and a passage of the nozzle part A valve body portion that changes both the cross-sectional area and the passage cross-sectional area of the pressure reducing portion; and a drive mechanism portion that displaces the nozzle portion and the pressure reducing portion. Furthermore, the drive mechanism part is comprised with the mechanical mechanism which has a deformation member which deform | transforms according to the change of at least one of the temperature and pressure of a refrigerant | coolant.

Therefore, the ejector module can constitute an ejector having a variable nozzle portion and a variable aperture mechanism.

Accordingly, the nozzle section and the pressure reducing section can be displaced according to the load fluctuation of the applied ejector refrigeration cycle, and the passage sectional area of the nozzle section and the throttle opening of the variable throttle mechanism can be changed in conjunction with each other. . As a result, a high COP can be exhibited in the ejector refrigeration cycle regardless of load fluctuations.

Therefore, the ejector having the variable nozzle portion and the variable aperture mechanism can be integrated without increasing the size.

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.

For example, the drive mechanism unit includes an enclosed space forming member that forms an enclosed space in which a temperature-sensitive medium whose pressure changes with a change in temperature of the refrigerant downstream of the pressure increasing unit is enclosed. You may employ | adopt what deform | transforms according to the pressure of a medium.

Here, the refrigerant on the downstream side of the pressurizing unit means the refrigerant that has flowed out of the pressurizing unit.

Therefore, in a refrigeration cycle apparatus in which the compressor suction side is connected to the refrigerant outlet of the booster, the refrigerant downstream from the booster flows through the refrigerant flow path from the refrigerant outlet of the booster to the compressor inlet. Refrigerant is included. Further, in the refrigeration cycle apparatus in which the refrigerant suction port side is connected to the refrigerant outlet of the boosting unit, the refrigerant flowing through the refrigerant flow path from the refrigerant outlet of the boosting unit to the refrigerant suction port is included in the refrigerant downstream of the boosting unit. included.

It is a whole block diagram of the ejector-type refrigerating cycle of 1st Embodiment. It is an axial sectional view of the ejector module of the first embodiment. It is an axial sectional view of the ejector module of the second embodiment. It is an axial sectional view of an ejector module of a 3rd embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of other embodiment.

(First embodiment)
A first embodiment of the present disclosure will be described with reference to FIGS. 1 and 2. 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.

In the ejector refrigeration cycle 10, an HFC refrigerant (specifically, R134a) or an HFO refrigerant (specifically, R1234fy) is employed as the refrigerant, and the high pressure side refrigerant pressure of the cycle is equal to the critical pressure of the refrigerant. The subcritical refrigeration cycle is not exceeded. 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.

The high-pressure inlet 21 a side provided in the 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) a part of the cycle constituent devices constituting the ejector refrigeration cycle 10.

More specifically, the ejector module 20 of the present embodiment is obtained by integrating the branching unit 14, the ejector 15, the variable throttle mechanism 16 and the like among the cycle constituent devices.

The branch part 14 branches the flow of the refrigerant that has flowed out of the radiator 12, injects one of the branched refrigerants from the nozzle part 15a of the ejector 15, and causes the other branched refrigerant to flow out to the variable throttle mechanism 16. Fulfill. The branch portion 14 is formed by connecting a space formed in the body portion 21 of the ejector module 20 and a refrigerant passage.

The ejector 15 has a nozzle portion 15a that depressurizes and injects one of the refrigerants branched at the branching portion 14, and functions as a refrigerant decompression device. Further, the ejector 15 functions as a refrigerant circulation device that sucks and circulates the refrigerant from the outside by the suction action of the refrigerant injected from the refrigerant injection port 15b of the nozzle portion 15a. 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 portion 15a and the refrigerant sucked from the refrigerant suction port 21b formed in the body portion 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. The nozzle portion 15a of the ejector 15 is configured such that the 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, the detailed configuration of the ejector module 20 will be described with reference to FIG. The ejector module 20 includes a body part 21, a composite valve body part 22, a drive mechanism part 23, and the like.

The body portion 21 forms an outer shell of the ejector module 20 and forms part of constituent members such as the ejector 15 and the variable aperture mechanism 16. The body part 21 is formed by combining a plurality of constituent members such as the main body part 211, the nozzle body 212, and the diffuser body 213.

The body section 21 is provided with a plurality of refrigerant inlets and outlets such as a high pressure inlet 21a, a refrigerant suction port 21b, an ejector side outlet 21c, a throttle side outlet 21d, a low pressure inlet 21e, and a low pressure outlet 21f.

The high-pressure inlet 21 a is a refrigerant inlet through which high-pressure refrigerant that has flowed 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. The refrigerant suction port 21 b is a refrigerant inlet that sucks the refrigerant flowing out of the first evaporator 17.

The ejector-side outlet 21c is a refrigerant outlet that causes the refrigerant whose pressure has been increased by the diffuser portion 15c of the ejector 15 to flow out to the inlet side of the second evaporator 18. 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. The low-pressure outlet 21f is a refrigerant outlet that allows the refrigerant flowing into the ejector module 20 from the low-pressure inlet 21e to flow out to the suction port side of the compressor 11.

Among these refrigerant inlets and outlets, the high pressure inlet 21a, the refrigerant suction port 21b, the throttle side outlet 21d, the low pressure inlet 21e, and the low pressure outlet 21f are provided in the main body 211. The ejector side outlet 21 c is provided in the diffuser body 213.

The main body 211 is formed of a columnar or prismatic metal (in this embodiment, aluminum). A plurality of refrigerant passages are formed inside the main body 211. The main body 211 may be made of resin.

The nozzle body 212 is formed of a cylindrical metal (in this embodiment, stainless alloy or brass) that tapers in the refrigerant flow direction. The nozzle body 212 is fixed inside the diffuser body 213 by means such as press fitting. Furthermore, the outer peripheral side of the diffuser body 213 is fixed to the main body 211 by means such as press fitting.

The nozzle body 212 forms an inflow space 20d for allowing a high-pressure refrigerant to flow therein, and also forms a nozzle portion 15a for injecting the refrigerant by isentropically reducing the pressure. The cylindrical side surfaces of the nozzle body 212 and the diffuser body 213 are formed with inlet holes that allow the high-pressure refrigerant that has flowed out of the radiator 12 to flow into the inflow space 20d by communicating the inflow space 20d with the high-pressure inlet 21a. The inflow space 20d is formed in a cylindrical shape.

The nozzle portion 15 a is provided on one end side in the axial direction of the nozzle body 212. The refrigerant passage of the nozzle portion 15a is formed with a throat portion that reduces the refrigerant passage cross-sectional area, and a divergent portion in which the passage cross-sectional area gradually increases as it goes from the throat to the refrigerant injection port 15b that injects the refrigerant. Yes. That is, the nozzle portion 15a is configured as a Laval nozzle.

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

At the other end side in the axial direction of the inflow space 20d of the nozzle body 212, an inlet of the throttle passage 20a formed in the main body 211 is opened. For this reason, the high-pressure refrigerant that has flowed into the inflow space 20d of the nozzle body 212 from the high-pressure inlet 21a flows into both the nozzle portion 15a and the throttle passage 20a from the inflow space 20d. That is, in the present embodiment, the branch portion 14 is formed in the inflow space 20d of the nozzle body 212.

The throttle passage 20a is a decompression section that decompresses the refrigerant 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. That is, 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.

Furthermore, the central axis of the inflow space 20d, the central axis of the nozzle portion 15a, and the central axis of the throttle passage 20a are arranged coaxially with each other. Accordingly, the nozzle portion 15a and the throttle passage 20a of the present embodiment are arranged side by side in the axial direction of the nozzle portion 15a.

The diffuser body 213 is made of a cylindrical metal (in this embodiment, aluminum). The diffuser body 213 forms a diffuser portion 15c that is a pressure increasing portion for increasing the pressure of the mixed refrigerant of the injected refrigerant and the suction refrigerant. The cylindrical side surface of the diffuser body 213 is formed with a suction hole for allowing the refrigerant flowing out from the first evaporator 17 to flow into the diffuser portion 15c by communicating the diffuser portion 15c with the refrigerant suction port 21b.

The suction refrigerant sucked from the refrigerant suction port 21b is guided to a space on the outer peripheral side of the nozzle portion 15a of the nozzle body 212. The diffuser portion 15c is a refrigerant passage formed in a substantially truncated cone shape in which the passage cross-sectional area gradually increases as it goes downstream of the refrigerant flow. In the diffuser portion 15c, the kinetic energy of the mixed refrigerant can be converted into pressure energy by such a passage shape.

The composite valve body portion 22 is a valve body portion that changes both the passage sectional area of the nozzle portion 15a and the passage sectional area of the throttle passage 20a. The composite valve body portion 22 is formed in a columnar shape with the same metal as the nozzle portion 15a. The central axis of the composite valve body 22 is arranged coaxially with the central axis of the nozzle portion 15a and the central axis of the throttle passage 20a. The composite valve body portion 22 includes a needle valve portion 22a, a throttle valve portion 22b, and a connecting portion 22c.

Needle valve portion 22a is a portion that changes the passage cross-sectional area of nozzle portion 15a. The needle valve portion 22a is formed in a needle shape (or a shape in which a conical shape and a cylindrical shape are combined), and in the inflow space 20d of the nozzle portion 15a and in the refrigerant passage, in the direction of the central axis of the nozzle portion 15a. It is arranged to extend. The needle valve portion 22a is displaced toward the side closer to the refrigerant injection port 15b, thereby reducing the passage cross-sectional area of the nozzle portion 15a.

The throttle valve portion 22b is formed in a truncated cone shape whose outer diameter on the bottom side is larger than the outer diameter of the needle valve portion 22a, and is on the downstream side of the refrigerant flow in the throttle passage 20a (that is, the refrigerant injection port more than the throttle passage 20a). 15b). The throttle valve portion 22b, together with the needle valve portion 22a, is displaced toward the side closer to the refrigerant injection port 15b, thereby reducing the passage cross-sectional area (that is, the throttle opening) of the throttle passage 20a.

Furthermore, in this embodiment, the nozzle part 15a can also be obstruct | occluded by making the needle valve part 22a contact | abut to the throat part of the nozzle part 15a. Of course, the throttle passage 20a may be closed by bringing the throttle valve portion 22b into contact with the outlet of the throttle passage 20a. Further, both the nozzle portion 15a and the throttle passage 20a may be closed.

The connecting portion 22c is formed in a columnar shape whose outer diameter is smaller than the outer diameter of the throttle valve portion 22b, and extends in a direction away from the nozzle portion 15a than the throttle valve portion 22b. The drive mechanism 23 is connected to the end of the connecting portion 22c opposite to the nozzle portion 15a.

The drive mechanism section 23 displaces the composite valve body section 22 in the direction of the central axis of the nozzle section 15a. The drive mechanism unit 23 is configured by a mechanical mechanism.

More specifically, the drive mechanism unit 23 includes a temperature sensing unit 23a having a diaphragm 23b that is a deforming member that deforms according to the temperature and pressure of the refrigerant flowing out from the second evaporator 18. The deformation of the diaphragm 23b is transmitted to the connecting portion 22c of the composite valve body portion 22 so that the composite valve body portion 22 is displaced.

The temperature sensing part 23a has a case 23c which is a sealed space forming member that forms a sealed space 23d together with the diaphragm 23b. A temperature-sensitive medium that changes in pressure with changes in temperature is enclosed in the enclosed space 23d. In the present embodiment, the temperature-sensitive medium is mainly composed of a refrigerant circulating in the ejector refrigeration cycle 10.

The case 23c and the diaphragm 23b are formed in an annular shape around the central axis of the nozzle portion 15a. Therefore, the enclosed space 23d is also formed in an annular shape similar to the case 23c and the diaphragm 23b. The temperature sensing part 23 a is disposed in the accommodation space 20 b formed in the main body part 211. The accommodation space 20b communicates with the outflow side passage 20c that connects the low pressure inlet 21e and the low pressure outlet 21f.

For this reason, the pressure of the temperature-sensitive medium in the enclosed space 23d varies depending on the temperature of the low-pressure refrigerant flowing through the outflow side passage 20c (that is, the refrigerant flowing out of the second evaporator 18). And the diaphragm 23b 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 23d.

Therefore, it is desirable that the diaphragm 23b is made of a material that is rich in elasticity and excellent in pressure resistance and airtightness. Therefore, in the present embodiment, an annular metal thin plate made of stainless steel (SUS304) is employed as the diaphragm 23b. Furthermore, as the diaphragm 23b, rubber made of EPDM (ethylene propylene diene rubber) or HNBR (hydrogenated nitrile rubber) containing a base fabric (polyester) may be employed.

In the present embodiment, the enclosed space 23d is disposed closer to the nozzle portion 15a than the diaphragm 23b. Further, the connecting portion 22 c of the composite valve body portion 22 is connected to the surface on the opposite side of the nozzle portion 15 a of the diaphragm 23 b via the connecting member 24.

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 23d rises, and the outflow side passage from the pressure of the temperature sensitive medium in the enclosed space 23d. The pressure difference obtained by subtracting the pressure of the low-pressure refrigerant flowing through 20c increases. As a result, the diaphragm 23b is deformed to the side away from the nozzle portion 15a (the side on which the enclosed space 23d swells). As a result, the composite valve body portion 22 expands the passage cross-sectional area of the nozzle portion 15a and displaces the throttle passage 20a toward the side that increases the throttle opening.

On the other hand, when the temperature (superheat degree) 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 23d decreases, and the outflow side passage is determined from the pressure of the temperature sensitive medium in the enclosed space 23d. The pressure difference obtained by subtracting the pressure of the low-pressure refrigerant flowing through 20c becomes small. As a result, the diaphragm 23b is deformed to the side approaching the nozzle portion 15a (the side where the enclosed space 23d is contracted). As a result, the composite valve body 22 is displaced to reduce the passage cross-sectional area of the nozzle portion 15a and to reduce the throttle opening of the throttle passage 20a.

That is, the drive mechanism portion 23 can displace the composite valve body portion 22 according to the temperature and pressure of the refrigerant that has flowed out of the second evaporator 18. Therefore, the drive mechanism portion 23 of the present embodiment moves the composite valve body portion 22 so that the superheat degree of the refrigerant on the outlet side of the second evaporator 18 approaches a predetermined reference superheat degree (specifically, 1 ° C.). Displace.

The drive mechanism 23 reduces the passage cross-sectional area of the nozzle portion 15a and a coil spring 23e, which is an elastic member that applies a load that reduces the throttle opening of the throttle passage 20a. have. The reference superheat degree can be adjusted by changing the load of the coil spring 23e.

As is clear from the above description, in the ejector module 20, the nozzle part 15a of the nozzle body 212, the refrigerant suction port 21b of the main body part 211, the diffuser part 15c in the diffuser body 213, the needle valve part 22a of the composite valve body part 22, The ejector 15 having the variable nozzle portion configured to change the passage cross-sectional area of the nozzle portion 15a is configured by the drive mechanism portion 23 and the like.

Further, in the ejector module 20, the cross-sectional area of the throttle passage 20a (that is, the throttle opening) is changed by the throttle passage 20a of the main body 211, the throttle valve portion 22b of the composite valve body portion 22, the drive mechanism portion 23, and the like. A variable aperture mechanism 16 configured to be capable of being configured.

And when the drive mechanism part 23 displaces the composite valve body part 22, both the passage sectional area of the nozzle part 15a and the passage sectional area of the throttle passage 20a change in conjunction with each other. In the present embodiment, the nozzle portion 15a and the needle valve portion are set so that the passage area ratio between the passage cross-sectional area of the nozzle portion 15a and the passage cross-sectional area of the throttle passage 20a is an appropriate value determined according to the load fluctuation. The shapes of 22a, the throttle passage 20a, and the throttle valve portion 22b are set.

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 15c 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 exert its endothermic action.

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.

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 15a of the ejector 15, is isentropically decompressed, and is ejected from the refrigerant ejection port 15b. 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 drive mechanism unit 23 causes the superheat degree of the refrigerant flowing through the outflow side passage 20c (in other words, the refrigerant on the outlet side of the second evaporator 18) to approach the reference superheat degree (specifically, 1 ° C.). Next, the composite valve body 22 is displaced.

The injection refrigerant injected from the refrigerant injection port 15b of the nozzle portion 15a and the suction refrigerant sucked from the refrigerant suction port 21b flow into the diffuser portion 15c. In the diffuser portion 15c, 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 portion 15c 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. 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 outflow side passage 20c of the ejector module 20 and 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. The refrigerant decompressed by the variable throttle mechanism 16 flows out from the throttle-side outlet 21d and flows into the first evaporator 17. 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.

In this case, in the present embodiment, since the shapes of the nozzle portion 15a, the needle valve portion 22a, the throttle passage 20a, and the throttle valve portion 22b are set so that the passage area ratio becomes an appropriate value, the first evaporator The dryness of the refrigerant flowing out from 17 is about 0 °. The refrigerant flowing out from the first evaporator 17 is sucked from the refrigerant suction port 21b.

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 15 c 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 15c, and the refrigerant evaporation pressure in the first evaporator 17 is set by the nozzle unit 15a. 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, the ejector module 20 of the present embodiment includes an ejector 15 having a variable nozzle portion and a variable aperture mechanism 16. Accordingly, the passage sectional area of the nozzle portion 15a of the ejector 15 and the throttle opening of the variable throttle mechanism 16 can be changed in conjunction with each other according to the load fluctuation of the ejector refrigeration cycle 10.

At this time, since the passage area ratio between the passage sectional area of the nozzle portion 15a and the passage sectional area of the throttle passage 20a is set to an appropriate value, the flow rate of refrigerant flowing into the nozzle portion 15a and the variable throttle mechanism The flow rate of the refrigerant flowing into 16 can be adjusted appropriately. As a result, the ejector refrigeration cycle 10 can exhibit a high COP regardless of load fluctuations.

Further, the passage area ratio can be adjusted to an appropriate value, as in the ejector refrigeration cycle 10 of the present embodiment, the refrigerant flow is branched upstream of the nozzle portion 15a, and one of the branched refrigerants This is effective in a cycle configuration in which the refrigerant flows into the nozzle portion 15a and the other branched refrigerant is sucked from the refrigerant suction port 21b of the ejector 15 through the throttle mechanism and the evaporator.

The reason for this is that, in such a cycle configuration, when the flow rate of the circulating refrigerant circulating in the cycle decreases, such as during low-load operation, the refrigerant suction capacity of the ejector 15 decreases and the refrigerant is supplied to the first evaporator 17. Because it becomes difficult to do.

On the other hand, according to the ejector module 20 of the present embodiment, the passage area ratio can be adjusted to an appropriate value. Furthermore, according to the ejector refrigeration cycle 10 of the present embodiment, the refrigerant can be reliably supplied to the first evaporator 17 and the second evaporator 18 by using the suction and discharge action of the compressor 11. As a result, the first evaporator 17 and the second evaporator 18 can reliably exhibit the refrigerating capacity.

In addition, according to 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 configuration mechanism, the entire ejector refrigeration cycle 10 is integrated. As a result, it is possible to aim for miniaturization and productivity improvement.

However, in the ejector 15 having the variable nozzle portion and the variable throttle mechanism 16, a drive device (in this embodiment, the drive mechanism portion 23) for changing the passage sectional area or the throttle opening is required. Such a drive device is relatively large. 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 ejector 15 and the variable throttle mechanism 16 are integrated, the passage sectional area of the nozzle portion 15a of the ejector 15 and the aperture opening of the variable throttle mechanism 16 are opened. The degree is integrated so as to be adjusted by one common drive mechanism portion 23 and composite valve body portion 22.

Therefore, the ejector 15 and the variable aperture mechanism 16 are integrated with each other without causing an increase in size as compared with an ejector module having two drive mechanisms: a drive mechanism for the nozzle portion 15a and a drive mechanism for the variable aperture mechanism 16. It can be made. Further, since the drive mechanism portion 23 is configured by a mechanical mechanism, no electrical connection is required to displace the composite valve body portion 22.

As a result, 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.

Further, in the ejector module 20 of the present embodiment, the central axis of the nozzle portion 15a and the central axis of the throttle passage 20a are arranged coaxially. Therefore, a columnar member extending in the central axis direction of the nozzle portion 15a can be adopted as the composite valve body portion 22. According to this, while being able to form the composite valve body part 22 easily, the valve body part which changes the passage sectional area of the nozzle part 15a and the throttle opening degree of the variable throttle mechanism 16 simultaneously can be easily realized.

In the ejector module 20 of the present embodiment, the outflow side passage 20c is formed in the body portion 211 of the body portion 21, and the temperature sensing portion 23a of the drive mechanism portion 23 is in a space communicating with the outflow side passage 20c. Is arranged. According to this, the temperature sensing part 23a 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 temperature sensing portion 23a without causing the ejector module 20 to become large.

(Second Embodiment)
In the present embodiment, an example in which the ejector module 201 shown in FIG. 3 is employed with respect to the first embodiment will be described. In FIG. 3, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.

In the body part 21 of the ejector module 201, the main body part 211 and the diffuser body 213 are fixed to each other. The nozzle body 212 is slidably disposed in the central axis direction of the nozzle portion 15a in the internal space of the rotating body formed inside the main body portion 211 and the diffuser body 213.

A seal member (specifically, an O-ring) is interposed between the cylindrical outer peripheral surface of the nozzle body 212 and the inner peripheral surface of the diffuser body 213, and refrigerant does not leak from the gap between these members. . Further, in the present embodiment, the refrigerant suction port 21 b is provided in the diffuser body 213.

Further, the ejector module 201 includes an orifice member 25 formed of a bottomed cylindrical metal (aluminum in this embodiment) having a throttle passage 20a provided in the center. The orifice member 25 is disposed in a cylindrical internal space formed inside the main body 211 so as to be slidable in the direction of the central axis of the nozzle portion 15a.

A seal member (specifically, an O-ring) is interposed between the cylindrical outer peripheral surface of the orifice member 25 and the inner peripheral surface of the main body 211, and the refrigerant leaks from the gap between these members. Absent. Furthermore, the orifice member 25 is connected to the diaphragm 23b of the drive mechanism unit 23 through the connecting member 24 and a plate member 23f formed of a disk-like metal.

Further, the composite valve body portion 22 of the ejector module 201 is fixed to the main body portion 211 via a support member. Therefore, the composite valve body portion 22 of the ejector module 201 is not displaced with respect to the main body portion 211. Further, the central axis of the nozzle portion 15a, the central axis of the throttle passage 20a, the central axis of the orifice member 25, and the central axis of the composite valve body portion 22 are arranged coaxially with each other.

Further, the drive mechanism 23 of the ejector module 201 employs a case 23c and a diaphragm 23b that are formed in a circular shape when viewed from the central axis direction of the nozzle portion 15a. Further, the enclosed space 23d is disposed on the side farther from the nozzle portion 15a than the diaphragm 23b. The orifice member 25 is connected to the surface of the diaphragm 23b on the nozzle portion 15a side.

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 23d rises, and the outflow side passage from the pressure of the temperature sensitive medium in the enclosed space 23d. The pressure difference obtained by subtracting the pressure of the low-pressure refrigerant flowing through 20c increases. Thereby, the diaphragm 23b deform | transforms into the side (side where the enclosure space 23d swells) which approaches the nozzle part 15a. As a result, the nozzle body 212 and the orifice member 25 are displaced to enlarge the passage cross-sectional area of the nozzle portion 15a and increase 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 outflow side passage 20c decreases, the saturation pressure of the temperature sensitive medium in the enclosed space 23d decreases, and the outflow side passage is determined from the pressure of the temperature sensitive medium in the enclosed space 23d. The pressure difference obtained by subtracting the pressure of the low-pressure refrigerant flowing through 20c becomes small. As a result, the diaphragm 23b is deformed to the side away from the nozzle portion 15a (the side in which the enclosed space 23d is recessed). As a result, the nozzle body 212 and the orifice member 25 are displaced to reduce the passage cross-sectional area of the nozzle portion 15a and reduce the throttle opening of the throttle passage 20a.

That is, the drive mechanism portion 23 of the ejector module 201 can displace the nozzle portion 15a and the throttle passage 20a according to the temperature and pressure of the refrigerant flowing out from the second evaporator 18. And the drive mechanism part 23 can change both the passage cross-sectional area of the nozzle part 15a and the passage cross-sectional area of the throttle passage 20a by displacing the nozzle part 15a and the throttle passage 20a.

Here, a gap is formed between the nozzle body 212 and the orifice member 25 of the present embodiment in the central axis direction of the nozzle portion 15a.

Therefore, when the temperature (superheat degree) of the low-pressure refrigerant flowing through the outflow side passage 20c rises, the drive mechanism unit 23 first displaces the orifice member 25 to the side that increases the throttle opening of the throttle passage 20a. When the orifice member 25 comes into contact with the nozzle body 212, the drive mechanism 23 displaces the nozzle body 212 together with the orifice member 25 to the side that increases the passage cross-sectional area of the nozzle portion 15a.

That is, in the ejector module 201, when the throttle opening degree of the throttle passage 20a is increased, the increase in the passage sectional area of the nozzle portion 15a can be delayed with respect to the throttle passage 20a.

This is because, like the ejector refrigeration cycle 10 of the present embodiment, the refrigerant flow is branched upstream of the nozzle portion 15a, and one of the branched refrigerants flows into the nozzle portion 15a to be branched. This is effective in a cycle configuration in which the other refrigerant is sucked from the refrigerant suction port 21b of the ejector 15 through the throttle mechanism and the evaporator.

Therefore, at the time of low load operation, the nozzle portion 15a is closed, and the compressor 11 → the radiator 12 → the ejector module 20 (specifically, the branch portion 14 → the variable throttle) by using the suction / discharge action of the compressor 11. Mechanism 16) → first evaporator 17 → ejector module 20 (specifically, diffuser portion 15c) → second evaporator 18 → ejector module 20 (specifically, outflow side passage 20c) → compressor 11 in this order. The refrigerant may be circulated to reliably supply the refrigerant to the first evaporator 17 and the second evaporator 18.

Of course, in a cycle in which the ejector 15 can exhibit a sufficient refrigerant suction capacity regardless of the load fluctuation of the ejector refrigeration cycle 10, the nozzle portion 15a is not provided with an axial gap between the nozzle body 212 and the orifice member 25. Further, the throttle passage 20a may be displaced integrally.

Other operations and configurations of the ejector refrigeration cycle 10 are the same as those in the first embodiment. Therefore, also in the ejector module 201 and the ejector type refrigeration cycle 10 of the present embodiment, the same effect as that of the first embodiment can be obtained.

Furthermore, since the drive mechanism portion 23 of the present embodiment employs the diaphragm 23b formed in a circular shape, it is easy to ensure the amount of displacement in the central axis direction of the nozzle body 212 and the nozzle portion 15a of the orifice member 25. Therefore, the passage cross-sectional area can be changed sufficiently without causing the nozzle portion 15a and the throttle passage 20a to expand in the radial direction.

(Third embodiment)
In the present embodiment, an example in which the ejector module 202 shown in FIG. 4 is employed with respect to the first embodiment will be described. As in the second embodiment, the ejector module 202 employs the drive mechanism portion 23 having a case 23c and a diaphragm 23b formed in a circular shape when viewed from the central axis direction of the nozzle portion 15a.

In the drive mechanism portion 23 of the ejector module 202, the enclosed space 23d is disposed on the side farther from the nozzle portion 15a than the diaphragm 23b. The diaphragm 23b is fixed to the main body 211 via a plate member 23f and a support member. Further, the composite valve body portion 22 is connected to the case 23 c via the connecting member 24.

Other configurations of the ejector module 201 are the same as those of the ejector module 20 described in the first embodiment.

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 23d rises, and the outflow side passage from the pressure of the temperature sensitive medium in the enclosed space 23d. The pressure difference obtained by subtracting the pressure of the low-pressure refrigerant flowing through 20c increases. As a result, the diaphragm 23b is deformed and the enclosed space 23d is expanded. As a result, the composite valve body portion 22 together with the case 23c is displaced toward the side that increases the passage sectional area of the nozzle portion 15a and increases 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 outflow side passage 20c decreases, the saturation pressure of the temperature sensitive medium in the enclosed space 23d decreases, and the outflow side passage is determined from the pressure of the temperature sensitive medium in the enclosed space 23d. The pressure difference obtained by subtracting the pressure of the low-pressure refrigerant flowing through 20c becomes small. As a result, the diaphragm 23b is deformed and the enclosed space 23d is contracted. As a result, the composite valve element 22 together with the case 23c is displaced toward the side where the passage sectional area of the nozzle portion 15a is reduced and the throttle opening of the throttle passage 20a is reduced.

That is, the drive mechanism portion 23 of the ejector module 202 can displace the composite valve body portion 22 according to the temperature and pressure of the refrigerant flowing out from the second evaporator 18 as in the first embodiment. The drive mechanism 23 can change both the passage cross-sectional area of the nozzle portion 15a and the passage cross-sectional area of the throttle passage 20a in conjunction with each other.

Other configurations and operations of the ejector refrigeration cycle 10 are the same as those in the first embodiment. Therefore, also in the ejector module 201 and the ejector type refrigeration cycle 10 of the present embodiment, the same effect as that of the first embodiment can be obtained.

Furthermore, since the drive mechanism portion 23 of the present embodiment employs a circular diaphragm 23b, as in the second embodiment, the nozzle portion 15a and the throttle passage 20a are expanded in the radial direction. The passage cross-sectional area can be sufficiently changed without any problem.

(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) The

ejector modules

20, 201, and 202 are not limited to those disclosed in the above-described embodiment.

For example, in the above-described embodiment, the example in which the diaphragm 23b formed in a thin plate shape is employed as the deformable member has been described, but the deformable member is not limited to this. A bottomed cylindrical bellows formed of a bottomed cylindrical (cup-shaped) metal as the deformable member and having a bellows part that can be expanded and contracted in the displacement direction of the composite valve body part 22 may be employed. Moreover, you may employ | adopt the bellophram formed with the bottomed cylindrical rubber as a deformation | transformation member.

Moreover, although the above-mentioned embodiment demonstrated the example which employ | adopted what displaces the composite valve body part 22 grade | etc., According to the temperature and pressure of the refrigerant | coolant which flowed out from the 2nd evaporator 18 as a drive mechanism part, The mechanism is not limited to this. As the drive mechanism part, one that deforms the deformable member with a thermo wax that changes in volume according to the temperature change of the refrigerant, or one that has a deformable member formed of a shape memory alloy that deforms according to the temperature change of the refrigerant is adopted. Also good.

(3) The ejector refrigeration cycle to which the

ejector modules

20, 201, 202 can be applied is not limited to that disclosed in the above-described embodiment.

For example, an intermediate pressure depressurization device is added to the ejector refrigeration cycle 10 to depressurize the refrigerant flowing out of the radiator 12 until it becomes an intermediate pressure refrigerant in a gas-liquid two-phase state and to flow out to the high pressure inlet 21a side of the ejector module. Also good.

According to this, the gas-liquid mixed state refrigerant in which the gas-phase refrigerant and the liquid-phase refrigerant are homogeneously mixed can be flowed into the high-pressure inlet 21a of the ejector module. Therefore, the fluctuation of the flow rate ratio of the refrigerant flow branched at the branching portion 14 is suppressed when the refrigerant in which the gas-phase refrigerant and the liquid-phase refrigerant are unevenly mixed and inhomogeneously mixed flows into the high-pressure inlet 21a. Can do.

Further, a low-pressure accumulator that separates the gas-liquid refrigerant flowing out of the second evaporator 18 and flows out the separated gas-phase refrigerant to the suction side of the compressor may be added to the ejector refrigeration cycle 10.

Further, the

ejector modules

20, 201, 202 may be applied to the ejector refrigeration cycle 30 shown in the overall configuration diagram of FIG.

Specifically, the ejector refrigeration cycle 30 includes a compressor 11 that compresses and discharges a refrigerant, a radiator 12 that dissipates heat from the refrigerant discharged from the compressor 11, and a gas-liquid separator 31 that separates the gas and liquid of the refrigerant. The decompression device 32 that decompresses the liquid-phase refrigerant separated by the gas-liquid separator 31, the first evaporator 17 that evaporates the refrigerant decompressed by the decompression device 32, and the refrigerant decompressed by the decompression unit are evaporated The second evaporator 18, and the merge section 33 that merges the gas-phase refrigerant separated by the gas-liquid separator 31 and the refrigerant that has flowed out of the second evaporator 18 to flow out to the suction side of the compressor 11. ing.

In the ejector refrigeration cycle 30, the outlet side of the radiator 12 is connected to the high pressure inlet 21a of the ejector module 20, the refrigerant outlet side of the first evaporator 17 is connected to the refrigerant suction port 21b, and the ejector side outlet 21c is connected. The inlet side of the gas-liquid separator 31 is connected, and the refrigerant inlet side of the second evaporator 18 is connected to the throttle side outlet 21d.

Furthermore, in the first evaporator 17 of the ejector-type refrigeration cycle 30, heat exchange is performed between the low-pressure refrigerant decompressed by the decompression device 32 and the blown air blown from the first blower 17a. In the second evaporator 18, heat exchange is performed between the low-pressure refrigerant decompressed by the variable throttle mechanism 16 and the blown air blown from the second blower 18a.

Further, in the ejector refrigeration cycle 30, the refrigerant outlet of the junction 33 is directly connected to the suction side of the compressor 11, the refrigerant outlet of the first evaporator 17 is connected to the low pressure inlet 21e side, and the low pressure outlet 21f is sucked of refrigerant. You may connect to the port 21b. According to this, the superheat degree of the 1st evaporator 17 exit side refrigerant | coolant can be adjusted.

(4) Each component device constituting the

ejector refrigeration cycle

10, 30 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 above-described embodiment, an example in which a receiver-integrated condenser is employed as the radiator 12 has been described. Further, the radiator 12 has a supercooling unit that supercools the liquid-phase refrigerant flowing out from the receiver unit 12b. A so-called subcool condenser may be employed. In addition, a radiator 12 including only the condensing unit 12a, and a receiver (receiver) that separates the gas-liquid refrigerant flowing out of the radiator 12 and flows the separated liquid-phase refrigerant downstream. It may be adopted.

In the above-described embodiment, the example in which R134a or R1234yf is adopted as the refrigerant has been described, but the refrigerant is not limited to this. For example, 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.

In the ejector refrigeration cycle 10, the example in which the first evaporator 17 and the second evaporator 18 are integrally configured has been described. However, as in the ejector refrigeration cycle 30, the first evaporator 17 and the second evaporator 17 are configured. The vessel 18 may be configured separately. In the first evaporator 17 and the second evaporator 18, different refrigerant target fluids may be cooled in different temperature zones.

(5) Further, the means and components disclosed in the above-described embodiments may be appropriately combined within a feasible range. For example, the

ejector modules

201 and 202 described in the second and third embodiments may be applied to the ejector refrigeration cycle 30 described in FIG.

Claims

An ejector module applied to a vapor compression refrigeration cycle apparatus,
A nozzle part (15a) for injecting the refrigerant under reduced pressure;
A decompression section (20a) for decompressing the refrigerant;
A refrigerant suction port (21b) that sucks the refrigerant from the outside by the suction action of the jetted refrigerant jetted from the nozzle unit, and a boosting unit that boosts the mixed refrigerant of the jetted refrigerant and the sucked refrigerant sucked from the refrigerant suction port A body part (21) provided with (15c);
A valve body portion (22) for changing both the passage sectional area of the nozzle portion and the passage sectional area of the pressure reducing portion;
A drive mechanism (23) for displacing the valve body,
The drive mechanism section is an ejector module configured with a mechanical mechanism having a deformable member (23b) that deforms in response to a change in at least one of temperature and pressure of the refrigerant.
An ejector module applied to a vapor compression refrigeration cycle apparatus,
A nozzle part (15a) for injecting the refrigerant under reduced pressure;
A decompression section (20a) for decompressing the refrigerant;
A refrigerant suction port (21b) that sucks the refrigerant from the outside by the suction action of the jetted refrigerant jetted from the nozzle unit, and a boosting unit that boosts the mixed refrigerant of the jetted refrigerant and the sucked refrigerant sucked from the refrigerant suction port A body part (21) provided with (15c);
A valve body portion (22) for changing both the passage sectional area of the nozzle portion and the passage sectional area of the pressure reducing portion;
A drive mechanism section (23) for displacing the nozzle section and the decompression section,
The drive mechanism section is an ejector module configured with a mechanical mechanism having a deformable member (23b) that deforms in response to a change in at least one of temperature and pressure of the refrigerant.
The drive mechanism has an enclosed space forming member (23c) that forms an enclosed space (23d) in which a temperature-sensitive medium whose pressure changes with a change in temperature of the refrigerant downstream of the booster is enclosed,
The ejector module according to claim 1, wherein the deformable member is deformed according to a pressure of the temperature sensitive medium.
The valve body portion is formed in a shape extending in the axial direction of the nozzle portion,
The ejector module according to claim 1, wherein the nozzle part and the pressure reducing part are arranged side by side in the axial direction.
The refrigeration cycle apparatus includes a compressor (11) that compresses and discharges a refrigerant, a radiator (12) that dissipates the refrigerant discharged from the compressor, a first evaporator (17) that evaporates the refrigerant, and a refrigerant Having a second evaporator (18) that evaporates and flows out to the suction side of the compressor,
The outlet side of the radiator is connected to the high-pressure inlet (21a) through which the refrigerant flows into the nozzle part and the decompression part,
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,
The ejector module according to any one of claims 1 to 4, wherein a refrigerant inlet side of the first evaporator is connected to a throttle-side outlet (21d) through which the refrigerant flows out from the decompression unit.