JP6717276B2 - Ejector module - Google Patents

Description

The present invention relates to an ejector module to be applied to an ejector type 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 pressure increasing action of the ejector. As a result, in the ejector refrigeration cycle, it is possible to reduce the power consumption of the compressor and improve the coefficient of performance (COP) of the cycle.

Further, Patent Document 1 discloses an ejector-type refrigeration cycle applied to an air conditioner, which includes an evaporator unit. In the evaporator unit of Patent Document 1, among the constituent devices of the ejector type refrigeration cycle, a branch portion, an ejector, a fixed throttle, a first evaporator, a second evaporator and the like are integrated (in other words, unitized or modularized). It was made.

More specifically, the branch part branches the flow of the high-pressure refrigerant flowing out from the radiator, and causes the flow to the nozzle part side and the fixed throttle side of the ejector. The second evaporator is a heat exchanger that evaporates the refrigerant that has flowed from the diffuser portion of the ejector by exchanging heat with the blast air that is blown to the air-conditioned space, and the evaporated refrigerant flows 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 exchanging heat with the air blown after passing through the second evaporator, and the evaporated refrigerant flows out to the refrigerant suction port side of the ejector. Let

In the evaporator unit of Patent Document 1, by integrating a part of the cycle constituent devices as described above, the ejector type refrigeration cycle applied as a whole is miniaturized and productivity is improved.

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, if a load fluctuation occurs in the applied ejector type 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, if a load fluctuation occurs in the ejector type refrigeration cycle, the ejector will not be able to exert a sufficient pressurizing action, or the suction action of the ejector will decrease and it will not be possible to supply the refrigerant with an appropriate flow rate to the evaporator. Sometimes. As a result, in the evaporator unit of Patent Document 1, if a load fluctuation occurs in the ejector refrigeration cycle, the COP improving effect described above cannot be sufficiently obtained.

On the other hand, in Patent Document 1, instead of the fixed throttle, a variable throttle mechanism configured to be able to change the passage cross-sectional area (that is, throttle opening) may be adopted, 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 may be adopted as the above.

According to this, the throttle opening of the variable throttle mechanism or the passage cross-sectional area of the nozzle part is adjusted according to the load fluctuation of the ejector refrigeration cycle, and the refrigerant flow rate into the variable throttle mechanism and the refrigerant flow rate into the nozzle part are adjusted. Can be adjusted appropriately. Therefore, it is possible to cause the ejector to exert a sufficient pressure increasing action and to exert sufficient refrigerating capacity in both evaporators irrespective of load fluctuations, and to exert a high COP in the ejector refrigeration cycle.

However, if a variable diaphragm mechanism is adopted instead of the fixed diaphragm, a driving device for changing the diaphragm opening is required. This is also the case when the variable nozzle unit is used as the nozzle unit of the ejector. This type of drive device is relatively large in size. Furthermore, a general ejector is formed in an elongated cylindrical shape extending in the axial direction of the nozzle portion.

For this reason, the unit (or module) in which the constituent devices including the variable aperture mechanism and the ejector are integrated in a state where the variable aperture mechanism and the ejector are arranged so as not to interfere with each other is likely to be large. As a result, the miniaturization effect of the ejector type refrigeration cycle as a whole due to the integration of the constituent devices is impaired.

Further, when the ejector, the fixed throttle, the first evaporator, the second evaporator, and the like are integrated as in the evaporator unit of Patent Document 1, vibration when depressurizing the refrigerant by the nozzle portion or the fixed throttle of the ejector is generated. Is transmitted to the first evaporator and the second evaporator, and the refrigerant passing sound is likely to be loud. Further, since the evaporator unit is arranged on the indoor side, which is the space to be air-conditioned, such a refrigerant passing sound is likely to be offensive to the user.

In view of the above point, without increasing the size of the applied ejector type refrigeration cycle, the purpose is to provide an ejector module capable of changing the cross-sectional area.

In order to achieve the above object, the invention according to claim 1 is such that a compressor (11) for compressing and discharging a refrigerant, a radiator (12) for radiating the refrigerant discharged from the compressor, and a refrigerant for evaporating the refrigerant. An ejector module applied to an ejector-type refrigeration cycle (10) having one evaporator (17) and a second evaporator (18) for evaporating a refrigerant to flow to the suction side of a compressor,
A nozzle part (51) for depressurizing and ejecting a part of the refrigerant flowing out from the radiator, a depressurizing part (20a) for depressurizing another part of the refrigerant flowing out of the radiator, and a nozzle. A mixed refrigerant of a body portion (21) having a refrigerant suction port (21b) for sucking the refrigerant from the outside by the suction action of the jet refrigerant injected from the portion, and a jet refrigerant and a suction refrigerant sucked from the refrigerant suction port A pressure reducing portion (52) for increasing the pressure, a pressure reducing side valve body portion (61) for changing the passage cross-sectional area of the pressure reducing portion, and a pressure reducing side drive portion (62) for displacing the pressure reducing side valve body portion ,
The refrigerant inlet side of the first evaporator is connected to the throttle side outlet (21d) through which the refrigerant flows out from the pressure reducing section, the refrigerant outlet side of the first evaporator is connected to the refrigerant suction port, and the refrigerant flows out from the pressure increasing section. The refrigerant inlet side of the second evaporator is connected to the ejector side outlet (21c),
At least the pressure reducing portion of the nozzle portion and the pressure reducing portion is configured to be able to change the passage cross-sectional area, and at least a part of the pressure raising portion is provided inside at least one of the first evaporator and the second evaporator or the first evaporator. The pipe (19) connected to at least one of the container and the second evaporator, and is arranged so as to project from the body portion ,
A suction side passage (20b) is formed in the body portion to allow the refrigerant flowing out of the first evaporator to flow therethrough, and the pressure reducing side drive portion is deformed according to the temperature and pressure of the refrigerant flowing out of the first evaporator. The pressure reducing side temperature sensing portion (62a) having the pressure reducing side deforming member (62b) is disposed, and at least a part of the pressure reducing side temperature sensing portion is arranged in the suction side passage or in the space communicating with the suction side passage. is an ejector module that is.

According to this, it is possible to change the passage cross sectional area of at least reducing pressure portion (20a). Then, the flow rate of the refrigerant flowing into the nozzle section (51) and the flow rate of the refrigerant flowing into the pressure reducing section (20a) can be appropriately adjusted according to the load fluctuation of the ejector refrigeration cycle (10). As a result, the ejector type refrigeration cycle (10) can exhibit a high coefficient of performance (COP) regardless of load fluctuations.

Further, since the nozzle portion (51), the body portion (21) and the booster portion (52) are provided, the ejector (15) can be configured. Then, the pressurizing unit (52) is connected to the inside of at least one of the first evaporator (17) and the second evaporator (18) or to at least one of the first evaporator (17) and the second evaporator (18). It can be housed inside the pipe (19). Therefore, it is possible to prevent the applied ejector-type refrigeration cycle (10) from becoming large as a whole.

That is, according to the invention described in claim 1, it is possible to provide the ejector module configured so that the passage cross-sectional area can be changed without causing an increase in the size of the applied ejector-type refrigeration cycle (10).

It should be noted that the reference numerals in parentheses for each means described in this column and the claims are examples showing the correspondence with specific means described in the embodiments described later.

It is a typical whole block diagram of the ejector type freezing cycle of a 1st embodiment. It is an axial direction sectional view containing a nozzle part side central axis of an ejector module of a 1st embodiment. FIG. 3 is an axial cross-sectional view including the pressure reducing side central axis of the ejector module of the first embodiment. It is a side view of the ejector module of 1st Embodiment. It is a top view of the ejector module of 1st Embodiment. It is a partially exploded perspective view for explaining the integration of the evaporator unit of a 1st embodiment. FIG. 3 is a schematic side view for explaining a connection state between the ejector module of the first embodiment and a collective pipe. FIG. 3 is a schematic top view for explaining a connection state between the ejector module of the first embodiment and a collective pipe. It is an axial 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 a partially exploded perspective view for explaining integration of an evaporator unit of a 2nd embodiment. It is a typical side view for explaining a connection state of an ejector module and a 2nd evaporator of a 3rd embodiment.

(First embodiment)
1st Embodiment of this invention is described using FIGS. As shown in the overall configuration diagram of FIG. 1, the ejector module 20 of the present embodiment is applied to an ejector refrigeration cycle 10 which is a vapor compression refrigeration cycle device including an ejector as a refrigerant decompression device. The ejector-type refrigeration cycle 10 is applied to a vehicle air conditioner and has a function of cooling blown air that is blown into a vehicle compartment that is a cooling target space. Therefore, the cooling target fluid of the ejector type refrigeration cycle 10 is blown air.

The ejector-type refrigeration cycle 10 uses an HFC-based refrigerant (specifically, R134a) as a refrigerant, and constitutes a subcritical refrigeration cycle in which the refrigerant pressure on the high-pressure side does not exceed the critical pressure of the refrigerant. Further, refrigerating machine 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.

Of the components of the ejector refrigeration cycle 10, the compressor 11 sucks the refrigerant, compresses it until it becomes a high-pressure refrigerant, and discharges it. More specifically, the compressor 11 of the present embodiment is an electric compressor configured by housing a fixed displacement type compression mechanism and an electric motor for driving 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 adopted. The operation of the electric motor (the number of rotations) is controlled by a control signal output from an air conditioning controller (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-radiating heat exchanger that radiates and cools the high-pressure refrigerant by exchanging heat between the high-pressure side 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 condenser section 12a and a receiver section 12b. The condensing unit 12a is a heat exchange unit for condensation that causes the high-pressure gas-phase refrigerant discharged from the compressor 11 and the outside air blown from the cooling fan 12c to exchange heat with each other to radiate and condense the high-pressure gas-phase refrigerant. .. The receiver unit 12b is a refrigerant container that separates the gas-liquid of the refrigerant flowing out from the condensing unit 12a and stores the excess liquid phase refrigerant.

The cooling fan 12c is an electric blower whose rotation speed (blowing air amount) is controlled by a control voltage output from the air conditioning controller.

The refrigerant outlet of the receiver portion 12b of the radiator 12 is connected to the high pressure inlet 21a side provided in the body portion 21 of the ejector module 20. The ejector module 20 is an integrated (in other words, modularized) cycle component device enclosed by a broken line in FIG. More specifically, the ejector module 20 is one in which the branch portion 14, the ejector 15, the variable diaphragm mechanism 16 and the like are integrated.

The branch part 14 branches the flow of the refrigerant flowing out from the radiator 12, causes one of the branched refrigerants to flow toward the nozzle part 51 side of the ejector 15, and the other branched refrigerant to the inlet side of the variable throttle mechanism 16. Fulfill the function of draining to. 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 has a nozzle portion 51 that decompresses and injects one of the refrigerant branched by the branch portion 14, and functions as a refrigerant pressure reducing device. Further, the ejector 15 functions as a refrigerant circulation device that sucks the refrigerant from the outside and circulates it by the suction action of the injected refrigerant ejected from the nozzle portion 51. More specifically, the ejector 15 sucks the refrigerant flowing out from the first evaporator 17 described later.

In addition to this, the ejector 15 converts the kinetic energy of a mixed refrigerant of the injection refrigerant injected from the nozzle portion 51 and the suction refrigerant sucked from the refrigerant suction port 21b formed in the body portion 21 into pressure energy. , And functions as an energy conversion device that pressurizes 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. Further, the nozzle portion 51 is a variable nozzle portion configured so that the passage cross-sectional area can be changed.

The variable throttle mechanism 16 has a throttle passage 20a that reduces the pressure of the other refrigerant branched by the branch portion 14. The variable throttle mechanism 16 is configured to be able to change the passage cross-sectional area (that is, the throttle opening degree) of the throttle passage 20a. The variable throttle mechanism 16 causes the depressurized 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. 1. The upper and lower arrows in FIGS. 2 to 4 indicate the respective upper and lower directions when the ejector-type refrigeration cycle 10 is mounted in a vehicle air conditioner. This also applies to the following drawings. 2 is a II-II sectional view of FIGS. 4 and 5, and FIG. 3 is a III-III sectional view of FIGS. 4 and 5. FIG. 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.

In order to simplify the drawing and clarify the description, the refrigerant flow direction in the ejector 15 shown in the overall configuration diagram of FIG. 1 and the refrigerant flow direction in the ejector 15 shown in FIGS. 2 and 5 are different directions. Has become.

The body portion 21 is formed by combining a plurality of metal (in the present embodiment, aluminum) constituent members. The body portion 21 forms an outer shell of the ejector module 20, and also functions as a housing that houses constituent members such as the ejector 15 and the variable diaphragm mechanism 16 therein. In other words, the branch portion 14 and the variable aperture mechanism 16 are formed integrally with the body portion 21 of the ejector 15. The body portion 21 may be made of resin.

Inside the body portion 21, various refrigerant passages 20a to 20c described later are formed. The body portion 21 is provided with a plurality of refrigerant inlets/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 portion of the refrigerant flow in a diffuser portion 52 of the ejector 15 which will be described later and is fixed to the body portion 21.

As shown in FIG. 3, the high-pressure inlet 21 a is a refrigerant inlet that allows the refrigerant flowing out of the refrigerant outlet of the receiver 12 b of the radiator 12 to flow into the ejector module 20. Therefore, the high pressure inlet 21 a serves as the refrigerant inlet of the branch portion 14.

As shown in FIG. 3, the refrigerant suction port 21b is a refrigerant inlet for sucking the refrigerant flowing out from the first evaporator 17. The suction refrigerant sucked from the refrigerant suction port 21b merges with the jet refrigerant jetted from the nozzle portion 51. Therefore, the suction-side passage 20b is a refrigerant passage through which the suction refrigerant sucked from the refrigerant suction port 21b flows and joins with the jet refrigerant.

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 to the inlet side of the second evaporator 18. As shown in FIG. 3, the throttle-side outlet 21d is a refrigerant outlet that causes the refrigerant whose pressure has been reduced by the variable throttle mechanism 16 to flow to the inlet side of the first evaporator 17.

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

Further, the high pressure inlet 21a and the low pressure outlet 21f are open in the same direction on the same plane as shown in FIGS. The ejector side outlet 21c, the low pressure inlet 21e, the refrigerant suction port 21b, and the throttle side outlet 21d are 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 fact that the refrigerant inlet and outlet are open in the same direction means that the refrigerant inflow and outflow directions are the same.

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

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

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

Further, in the present embodiment, as the nozzle portion 51, one that is set so that the flow velocity of the injected refrigerant injected from the refrigerant injection port is equal to or higher than the sonic speed during the normal operation of the ejector refrigeration cycle 10 is adopted. Of course, the nozzle portion 51 may be formed by a tapered nozzle portion.

An inlet hole is formed on the cylindrical side surface of the nozzle portion 51 to allow one of the refrigerants branched by the branch portion 14 to flow into the refrigerant passage. Further, the above-mentioned suction side passage 20b 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 booster that boosts the pressure of the mixed refrigerant. The diffuser portion 52 is formed of a cylindrical metal (aluminum in this embodiment). The diffuser portion 52 of the present embodiment is fixed to the body portion 21 by means such as press fitting. A vibration damping member made of rubber or resin may be interposed between the diffuser portion 52 and the body portion 21. Further, the diffuser portion 52 may be integrally formed with the same member as the body portion 21.

The refrigerant passage formed inside the diffuser portion 52 is formed in a substantially frustoconical shape whose passage cross-sectional area gradually increases toward the refrigerant flow downstream side. 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 projects from the body portion 21 toward the refrigerant flow downstream side. Therefore, the ejector-side outlet 21c formed in the most downstream portion of the diffuser portion 52 in the refrigerant flow is, as shown in FIGS. 2 and 3, a plane different from the refrigerant suction port 21b, the throttle-side outlet 21d, and the low-pressure inlet 21e. It opens at the top.

The needle valve 53 is a nozzle portion side valve body portion that changes the passage 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 portion 51 and the central axis of the refrigerant passage of the diffuser portion 52. The needle valve 53 changes the passage cross-sectional area of the refrigerant passage of the nozzle portion 51 by being displaced in the central axis direction. Further, the nozzle portion 51 can be closed by bringing the needle valve 53 into contact with the throat portion of the nozzle portion 51.

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

More specifically, the nozzle unit side drive mechanism 54 is a nozzle unit side deforming member (specifically, a nozzle unit side diaphragm 54b) that deforms according to the temperature and pressure of the refrigerant flowing out from the second evaporator 18. The temperature sensor 54a having a nozzle 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 the temperature-sensitive medium whose pressure changes with temperature changes is enclosed in the nozzle-side temperature-sensitive portion 54a. In the present embodiment, as the temperature sensitive medium, a medium whose main component is a refrigerant that circulates in the ejector refrigeration cycle 10.

The nozzle-side temperature sensitive portion 54a is arranged in a space formed in the body portion 21 and communicating with the outflow-side passage 20c. Therefore, 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 flowing out from the second evaporator 18) flowing through the outflow passage 20c. Then, the diaphragm 54b is deformed according to the pressure difference between the pressure of the low-pressure refrigerant flowing through the outflow passage 20c and the pressure of the temperature-sensitive medium in the enclosed space 54c.

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

Further, in the nozzle portion side drive mechanism 54 of the present embodiment, a part of the diaphragm 54b is fixed to the body portion 21. The needle valve 53 is fixed to the case. The case 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 passage 20c rises, the saturation pressure of the temperature-sensitive medium in the enclosed space 54c rises, and the pressure of the temperature-sensitive medium in the enclosed space 54c increases from the outflow passage. The pressure difference obtained by subtracting the pressure of the low-pressure refrigerant flowing through 20c becomes large. As a result, the diaphragm 54b is deformed to the side where the enclosed space 54c swells. As a result, the needle valve 53 is displaced to the side of increasing the passage cross-sectional area of the nozzle portion 51 (that is, the side away from the throat portion).

On the other hand, when the temperature (superheat) of the low-pressure refrigerant flowing through the outflow passage 20c decreases, the saturation pressure of the temperature-sensitive medium in the enclosed space 54c decreases, and the pressure of the temperature-sensitive medium in the enclosed space 54c decreases from the outflow passage. The pressure difference obtained by subtracting the pressure of the low-pressure refrigerant flowing through 20c is reduced. As a result, the diaphragm 54b is deformed so that the enclosed space 54c contracts. As a result, the needle valve 53 is displaced to the side that reduces the passage cross-sectional area of the nozzle portion 51 (that is, the side closer to the throat portion).

That is, the nozzle unit side drive mechanism 54 can displace the needle valve 53 according to the degree of superheat of the refrigerant flowing out from the second evaporator 18. Therefore, the nozzle unit-side drive mechanism 54 of the present embodiment is arranged so that the superheat degree of the refrigerant on the outlet side of the second evaporator 18 approaches the predetermined nozzle unit side reference superheat degree (specifically, 1° C.). The valve 53 is displaced.

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

Here, when the nozzle section side drive mechanism 54 defines the center axis in the displacement direction that displaces the needle valve 53 as the nozzle section side center axis CL1, the nozzle section side center axis CL1 is the center axis of the nozzle section 51 and the needle valve. The central axis of 53 and the central axis of the diffuser portion 52 coincide with each other.

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 pressure reducing portion that reduces the pressure of the other refrigerant branched by the branch portion 14 by reducing the passage cross-sectional area. The throttle passage 20a is formed in a rotating body shape such as a cylindrical shape or a truncated cone shape. The decompression section of the present embodiment is formed integrally with the body section 21. An orifice formed as a separate member from the body portion 21 may be adopted as the depressurizing portion, and the orifice may be integrally fixed to the body portion 21 by means of press fitting or the like.

The throttle valve 61 is formed in a spherical shape, and is a pressure reducing valve body that changes the passage cross-sectional area (that is, throttle opening) of the throttle passage 20a by being displaced in the central axis direction of the throttle passage 20a. Further, 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 drive mechanism 62 is a pressure reducing side drive unit that displaces the throttle valve 61 in the central axis direction of the throttle passage 20a. The pressure reducing side drive mechanism 62 is configured by a mechanical mechanism similar to the nozzle unit side drive mechanism 54.

More specifically, the pressure reducing side drive mechanism 62 has a pressure reducing side deforming member (specifically, a pressure reducing side diaphragm 62b) that deforms according to the temperature and pressure of the refrigerant flowing out from the first evaporator 17. The side temperature sensing unit 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 depressurizing side drive mechanism 62, a part of the depressurizing side temperature sensitive portion 62a is arranged in the suction side passage 20b. Further, in the pressure reducing side drive mechanism 62 of the present embodiment, the displacement of the diaphragm 62b 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.

Then, 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 depressurization-side drive mechanism 62 rises, and the temperature-sensitive medium in the enclosed space 62c. The pressure difference of the pressure of the low-pressure refrigerant flowing through the suction side passage 20b from the pressure becomes large. As a result, when the diaphragm 62b is deformed, the throttle valve 61 is displaced to the side of increasing the throttle opening degree of the throttle passage 20a.

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

That is, the pressure reducing 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 unit side drive mechanism 54 of the present embodiment is configured so that the superheat degree of the refrigerant on the outlet side of the first evaporator 17 approaches the predetermined depressurization side reference superheat degree (specifically, 0° C.). To displace. That is, the nozzle unit side drive mechanism 54 of the present embodiment displaces the throttle valve 61 so that the first evaporator 17 outlet side refrigerant becomes the saturated vapor 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 portion-side reference superheat degree.

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

Further, in the ejector module 20 of the present embodiment, the nozzle portion side central axis CL1 and the pressure reducing side central axis CL2 have a twisted positional relationship, and one of the center of the nozzle portion side central axis CL1 and the pressure reducing side central axis CL2 is the center. When viewed in the axial direction, the drive portion corresponding to one central axis and the other central axis are superposed.

For example, as shown in FIG. 4, when viewed from the direction of the central axis CL1 of the nozzle portion, the nozzle portion side driving mechanism 54 and the central axis CL2 of the pressure reducing side which occupy the area shown by the dot hatching in FIG. Has been done. Further, as shown in FIG. 5, when viewed from the direction of the pressure-reducing side central axis CL2, the pressure-reducing side driving mechanism 62 and the nozzle side central axis CL1 occupying the area indicated by the dot hatching in FIG. ing.

The twisted positional relationship means a positional relationship in which two straight lines are not parallel and are arranged so as not to intersect with each other. Further, in the present embodiment, the angle formed by the nozzle portion side central axis CL1 and the pressure reducing side central axis CL2, that is, the angle formed by the vector of the nozzle portion side central axis CL1 and the vector of the pressure reducing side central axis CL2 is 90°. There is.

Next, in the second evaporator 18 shown in FIG. 1, the blown air blown from the blower 18a toward the passenger compartment 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 an endothermic heat exchanger that cools the blown air by exchanging heat with the low-pressure refrigerant flowing out from it and evaporating the low-pressure refrigerant to exert an endothermic effect.

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

The first evaporator 17 exchanges heat between the blast 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), and this low pressure It is an endothermic heat exchanger that cools blown air by evaporating a refrigerant to exert an endothermic effect. The refrigerant outlet of the first evaporator 17 is connected to the refrigerant suction port 21b side of the ejector module 20.

Further, the first evaporator 17 and the second evaporator 18 of this embodiment are integrally configured. Specifically, each of the first evaporator 17 and the second evaporator 18 includes a plurality of tubes through which a refrigerant flows, and a collection or distribution of the refrigerant that is disposed on both ends of the plurality of tubes and that flows through the tubes. It is composed of a so-called tank-and-tube type heat exchanger having a pair of collective distribution tanks for performing the above.

The first and second evaporators 17 and 18 are integrated by forming the collective distribution tank 181 of the first and second evaporators 17 and 18 with the same member. At this time, in the present embodiment, the first evaporator 17 and the second evaporator 18 are placed in the blast air flow so that the second evaporator 18 is arranged on the upstream side of the blast air flow with respect to the first evaporator 17. In contrast, they are arranged in series. Therefore, the blown air flows as shown by the arrow drawn by the chain double-dashed line in FIG.

Here, in the present embodiment, the collective distribution tank 181 of the first evaporator 17 and the second evaporator 18 is formed of the same member. Therefore, the collective distribution tank 181 is not limited to a part that functions as a collective distribution tank for the first evaporator 17 and a part that functions as a collective distribution tank for the second evaporator 18. An auxiliary tank or the like for communicating the spaces for collective distribution is also included.

This type of auxiliary tank also functions as a pipe connected to the collective distribution tank for the first evaporator 17 and the collective distribution tank for the second evaporator 18.

Further, in the present embodiment, between the refrigerant inlet/outlet ports 21b to 21e of the ejector module 20 and the refrigerant inlet/outlet ports of the integrated first evaporator 17 and second evaporator 18 are shown in FIGS. 6 to 8. As described above, the dedicated collecting pipe 19 is used for connection. Each refrigerant inlet/outlet of the first evaporator 17 and the second evaporator 18 is formed on one end side of the collective distribution tank 181 of the first evaporator 17 and the second evaporator 18.

A plurality of metallic refrigerant pipes of the collecting pipe 19 or plate members are integrated by joining means such as brazing. The collecting pipe 19 has first to fourth connection passages 19a to 19d. Of course, the collecting pipe 19 may be formed by providing a plurality of refrigerant passages in a block-shaped member such as a metal block or a resin block.

The first connection passage 19a is a refrigerant passage that connects the throttle-side outlet 21d 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 ejector-side outlet 21c and the refrigerant inlet of the second evaporator 18. 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.

Further, in the present embodiment, as shown in FIGS. 6 to 8, the nozzle portion side central axis CL1 (that is, the longitudinal direction of the diffuser portion 52) and the collective distribution tank of the first evaporator 17 and the second evaporator 18. The angle formed by the longitudinal direction of 181 is about 90°. Therefore, the collecting pipe 19 of the present embodiment is formed in a curved shape. Further, in the collecting pipe 19, the first to fourth connection passages 19a to 19d are formed in a bent shape.

Accordingly, the collecting pipe 19 redirects the flow direction of the refrigerant flowing out of the ejector module 20 toward the refrigerant inlet/outlet side of the first evaporator 17 and the second evaporator 18, and at the same time, the first evaporator 17 and the second evaporator 17 The flow direction of the refrigerant flowing out from the evaporator 18 is turned toward the refrigerant inlet/outlet ports 21b to 21e of the ejector module 20.

Furthermore, in the third connection passage 19c of the collecting pipe 19 of the present embodiment, a cylindrical space that fits the outer shape of the diffuser portion 52 is formed. The portion of the diffuser portion 52 protruding from the body portion 21 is housed in the third connection passage 19c. In other words, the diffuser portion 52 is formed so as to be accommodated in the collecting pipe 19 by protruding from the body portion 21.

Here, the collecting pipe 19 and the ejector module 20 are integrated by bolting or the like. Further, a gasket 191 as a sealing member is arranged between the collecting pipe 19 and the ejector module 20, so that the refrigerant does not leak from the gap between the ejector module 20 and the collecting pipe 19.

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

Then, in the evaporator unit 200, at least a part of the diffuser portion 52 is housed in the third connection passage 19c of the collecting pipe 19. Further, the nozzle portion 51 and the throttle passage 20a are arranged outside the first evaporator 17 and the second evaporator 18 and outside the collecting pipe 19.

Next, the electric control unit of the ejector type refrigeration cycle 10 of the present embodiment will be described. The air-conditioning control device (not shown) is composed of a well-known microcomputer including a CPU, a ROM, a RAM and the like and its peripheral circuits, performs various calculations and processing based on a control program stored in the ROM, and is connected to the output side. It controls the operation of the various controlled devices 11, 12c, 18a and the like.

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 from the first evaporator 17. A sensor group such as an evaporator temperature sensor that detects (evaporator temperature) is connected, and the detection values of these air conditioning sensor groups are input.

Further, 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 for requesting air conditioning, a vehicle interior temperature setting switch for setting the vehicle interior temperature, and the like are provided.

The air-conditioning control device of the present embodiment has a control unit integrally configured to control the operation of various control target devices connected to the output side thereof. The configuration (hardware and software) that controls the operation of the device constitutes the control unit of each controlled device. For example, in the present embodiment, the configuration that controls the operation of the compressor 11 constitutes the discharge capacity control means.

Next, the operation of the ejector-type 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.

As a result, the compressor 11 draws in the refrigerant, compresses it, and discharges it. The high-temperature high-pressure refrigerant discharged from the compressor 11 flows into the radiator 12. The refrigerant flowing into the radiator 12 heat-exchanges with the outside air blown from the cooling fan 12c in the condenser 12a and is condensed. The refrigerant cooled in the condenser 12a is separated into gas and liquid in the receiver 12b.

The liquid-phase refrigerant separated by the receiver portion 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 branch portion 14. One of the branched refrigerant flows into the nozzle portion 51 of the ejector 15 and is isentropically decompressed and injected. Then, the refrigerant that has flowed out of the first evaporator 17 is sucked through the refrigerant suction port 21b due to the suction action of the injected refrigerant.

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

The injection refrigerant injected from the nozzle portion 51 and the suction refrigerant sucked from the refrigerant suction port 21b flow into the diffuser portion 52 of the ejector 15. In the diffuser section 52, the velocity energy of the refrigerant is converted into pressure energy due to the expansion of the refrigerant passage area. As a result, the pressure of the mixed refrigerant of the injection refrigerant and the suction refrigerant rises. The refrigerant whose pressure has been increased in the diffuser portion 52 flows out from the ejector side outlet 21c.

The refrigerant flowing out of the ejector-side outlet 21c flows into the second evaporator 18 via the third connecting 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. As a result, the blown air blown by the blower 18a is cooled.

The refrigerant flowing out from the second evaporator 18 is sucked into the compressor 11 and compressed again via the fourth connection passage 19d of the collecting pipe 19 and the outflow passage 20c of the ejector module 20.

On the other hand, the other refrigerant branched at the branch portion 14 flows into the throttle passage 20a of the variable throttle mechanism 16 and is isenthalpically reduced in pressure. At this time, the depressurization-side drive mechanism 62 causes the superheat degree of the refrigerant flowing in the suction-side passage 20b (in other words, the outlet-side refrigerant of the first evaporator 17) to become the depressurization-side reference superheat degree (specifically, 0° C.). The throttle valve 61 is displaced so that it approaches. The refrigerant whose pressure has been reduced by the variable throttle mechanism 16 flows out from the throttle-side outlet 21d.

The refrigerant flowing out from the throttle-side outlet 21d flows into the first evaporator 17 via the first connection passage 19a of the collecting pipe 19. The refrigerant flowing into the first evaporator 17 absorbs heat from the blown air that has passed 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 of the first evaporator 17 is sucked from the refrigerant suction port 21b via the second connection passage 19b of the collecting pipe 19.

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

Further, in the ejector-type refrigeration cycle 10 of the present embodiment, the refrigerant on the downstream side of the second evaporator 18, that is, the refrigerant whose pressure is increased by the diffuser portion 52 of the ejector 15 can be sucked into the compressor 11. Therefore, in the ejector 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 and the suction refrigerant pressure are equal. Can be improved.

Further, in the ejector refrigeration cycle 10 of the present embodiment, the refrigerant evaporation pressure in the second evaporator 18 is set as the refrigerant pressure increased by the diffuser section 52, and the refrigerant evaporation pressure in the first evaporator 17 is set at the nozzle section 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 configured by the nozzle portion 51, the needle valve 53, the nozzle portion side drive mechanism 54, and the throttle passage 20a, the throttle valve 61, the pressure reducing side. The variable diaphragm mechanism 16 including the drive mechanism 62 and the like is provided.

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

Further, in the ejector module 20 of the present embodiment, among the cycle constituting mechanism, the branch portion 14, the ejector 15 having the variable nozzle portion, and the variable throttle mechanism 16 are integrated, so that the ejector type refrigeration cycle 10 as a whole. It is possible to reduce the size and improve the productivity.

However, in the ejector 15 having the variable nozzle portion and the variable throttle mechanism 16, the drive device (in the present embodiment, the nozzle portion side drive mechanism 54 and the pressure reducing side drive mechanism 62) for changing the passage sectional area or the throttle opening degree is provided. Will be required. Such a drive device is relatively large in size as compared with the needle valve 53, the throttle valve 61, and the like. Further, the ejector 15 is formed in an elongated cylindrical shape extending in the nozzle portion side central axis CL1 direction.

Therefore, if it is attempted to arrange the ejector 15 having the variable nozzle portion and the variable diaphragm mechanism 16 so as not to interfere with each other, it becomes difficult to obtain the effect of reducing the size of the ejector module 20 as a whole.

On the other hand, in the ejector module 20 of the present embodiment, at least a part of the diffuser portion 52 projects from the body portion 21 and is housed inside the collecting pipe 19. Therefore, it is possible to reduce the size of the ejector-type refrigeration cycle 10 as a whole. That is, according to the ejector module 20 of the present embodiment, even if the passage cross-sectional area of the nozzle portion 51 and the passage cross-sectional area of the throttle passage 20a are configured to be changeable, the size of the applied ejector refrigeration cycle 10 is increased. Will not be invited.

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 open 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 are 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 are opened in the same direction. Therefore, the ejector module 20 can be easily connected to the first evaporator 17 and the second evaporator 18.

That is, the ejector module 20 of the present embodiment functions as a joint portion (connection portion) of the evaporator unit 200, and the assembling property of the ejector refrigeration cycle 10 can be improved. Thereby, the productivity of the ejector-type refrigeration cycle 10 as a whole can be further improved.

Further, in the ejector module 20 of the present embodiment, when the variable throttle mechanism 16 and the ejector 15 are integrated, when viewed from the central axis direction of one of the nozzle portion side central axis CL1 and the pressure reducing side central axis CL2, The drive unit corresponding to one central axis and the other central axis are arranged so as to overlap with each other.

According to such an arrangement, the decompression-side drive mechanism 62 and the nozzle portion-side drive mechanism 54, which are relatively large in size, can be arranged so as to be offset from each other in one of the central axes CL1 and CL2. Therefore, the main body portion of the variable throttle mechanism 16 (that is, the portion excluding the pressure reducing side drive mechanism 62) and the main body portion of the ejector 15 (that is, the portion excluding the nozzle portion side drive mechanism 54) can be arranged close to each other.

Further, since the nozzle portion side central axis CL1 and the pressure reducing side central axis CL2 have a twisted positional relationship, the variable diaphragm mechanism 16 can be provided without causing the pressure reducing side driving mechanism 62 and the nozzle portion side driving mechanism 54 to interfere with each other. The main body of the ejector 15 and the main body of the ejector 15 can be effectively brought close to each other. Therefore, it is possible to further suppress the increase in size of the applied ejector-type refrigeration cycle 10.

Further, in the ejector module 20 of the present embodiment, the outflow 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 passage 20c. It is located in the space where

According to this, it is possible to bring the temperature sensing portion 54a on the nozzle side and the passage 20c on the outflow side closer to each other. Therefore, the temperature and pressure of the refrigerant flowing through the outflow passage 20c can be accurately transmitted to the nozzle-side temperature sensing portion 54a without increasing 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 sensitive portion 62a of the pressure reduction side drive mechanism 62 is arranged in the suction side passage 20b. ing.

According to this, the pressure reducing side temperature sensing portion 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 pressure reducing side temperature sensing portion 62a without increasing the size of the ejector module 20.

Further, in the ejector module 20 of the present embodiment, the pressure reducing side drive mechanism 62 displaces the throttle valve 61 so that the superheat degree of the refrigerant on the outlet side of the first evaporator 17 approaches 0°C. According to this, it is possible to prevent the dryness of the refrigerant flowing out of the first evaporator 17 from being excessively lowered and sucking the gas-liquid two-phase refrigerant having a low dryness from the refrigerant suction port 21b. .. Therefore, it is possible to suppress a decrease in the boosting performance of the ejector 15.

Further, it is possible to prevent the superheat degree of the refrigerant on the outlet side of the first evaporator 17 from being excessively increased, and to prevent a temperature distribution from being generated in the blown air cooled by the first evaporator 17. You can This means that, in the configuration in which the first evaporator 17 is arranged on the downstream side of the second evaporator 18 in the air flow, like the ejector-type refrigeration cycle 10 of the present embodiment, the temperature of the blower air as the entire ejector-type refrigeration cycle 10 This is effective in that the distribution can be easily suppressed.

Further, in the evaporator unit 200 of the present embodiment, at least part of the diffuser portion 52 of the ejector module 20 is housed in the third connection passage 19c of the collecting pipe 19, so that the evaporator unit 200 as a whole is small in size. Can be promoted.

In addition to this, the nozzle portion 51 and the throttle passage 20a are arranged outside the first evaporator 17 and the second evaporator 18 and outside the collecting pipe 19. Therefore, the vibration when depressurizing the refrigerant in the nozzle portion 51 and the throttle passage 20a is less likely to propagate to the first evaporator 17 and the second evaporator 18.

As a result, it is possible to prevent the refrigerant passing noise, which is annoying to the user, from becoming loud. That is, according to the evaporator unit 200 of the present embodiment, the refrigerant passing noise can be suppressed without causing a decrease in the COP of the ejector refrigeration cycle 10.

Further, in the ejector module 20 of this embodiment, the diffuser portion 52 and the body portion 21 are formed as separate members. Therefore, compared with the case where the diffuser portion 52 and the body portion 21 are formed of the same member, the vibration when depressurizing the refrigerant in the nozzle portion 51 and the throttle passage 20a is further increased. 2 It becomes difficult to propagate to the evaporator 18.

Further, in the evaporator unit 200 of this embodiment, the collecting pipe 19 is formed in a curved shape. When the ejector module 20, the first evaporator 17, the second evaporator 18, and the like are integrated as the evaporator unit 200, the degree of freedom of arrangement of the ejector module 20 with respect to the first evaporator 17 and the second evaporator 18 is increased. Can be improved.
(Second embodiment)
In the present embodiment, as compared with the first embodiment, an example in which the needle valve 53 of the ejector 15 and the nozzle portion side drive mechanism 54 are eliminated as shown in FIGS. 9 and 10 will be described.

That is, the nozzle portion 51 of the ejector 15 of the present embodiment is a fixed nozzle portion whose passage cross-sectional area does not change. 9 and 10 are drawings corresponding to FIGS. 2 and 5 described in the first embodiment, respectively. In FIGS. 9 and 10, the same or equivalent parts as those in the first embodiment are designated by the same reference numerals. This also applies to the following drawings.

As is clear from FIGS. 9 and 10, in the ejector module 20 of the present embodiment, the positional relationship between the ejector 15 and the variable diaphragm mechanism 16 is substantially the same as that of the first embodiment. That is, the central axis of the nozzle portion 51, which is the central axis CL1 of the nozzle portion, and the pressure-reducing side central axis CL2 are in a twisted positional relationship, and when viewed from the pressure-reducing side central axis CL2 direction, the cross-hatching in FIG. The depressurizing side drive mechanism 62 occupying the area shown and the central axis of the nozzle portion 51 are arranged so as to overlap with each other.

The other configurations and operations of the ejector module 20 and the ejector-type refrigeration cycle 10 are similar to those of the first embodiment. Therefore, also in the ejector type refrigeration cycle 10 of the present embodiment, the same effect as in the first embodiment can be obtained.

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, Also, both the flow rate of the refrigerant flowing into the nozzle portion 51 can be adjusted. As a result, the ejector-type refrigeration cycle 10 can exhibit a high COP regardless of load fluctuations.

Further, according to the ejector module 20 and the evaporator unit 200 of the present embodiment, at least a part of the diffuser portion 52 can be housed inside the collecting pipe 19, and like the first embodiment, the ejector refrigeration system. It is possible to reduce the size of the entire cycle 10.

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

Therefore, in the ejector-type refrigeration cycle 10 of the present embodiment, the gas-liquid refrigerant of the low-pressure refrigerant is separated between the low-pressure outlet 21f of the ejector module 20 and the suction inlet of the compressor 11 to separate the separated gas-phase refrigerant into the compressor. An accumulator may be arranged to flow out to the suction port of 11.

(Third Embodiment)
In the first embodiment, an example in which the portion of the diffuser portion 52 that protrudes from the body portion 21 is housed in the third connection passage 19c of the collecting pipe 19 has been described. However, in the present embodiment, FIG. 11 and FIG. As shown, it is housed in the collective distribution tank 181. Note that FIG. 11 is a partially exploded perspective view seen from the downstream side in the flow direction of blown air, and FIG. 12 is a side view seen from the upstream side in the flow direction of blown air.

That is, in the present embodiment, the collecting pipe 19 is eliminated, and the portion of the diffuser portion 52 protruding from the body portion 21 is housed inside the components of the first evaporator 17 and the second evaporator 18. .. The other configurations and operations of the ejector module 20 and the ejector-type refrigeration cycle 10 are similar to those of the first embodiment. Therefore, also in the ejector type refrigeration cycle 10 of the present embodiment, the same effect as in the first embodiment can be obtained.

More specifically, in the ejector-type refrigeration cycle 10, the diffuser portion 52 is housed inside the collecting pipe 19 having an appropriate shape according to the relative positional relationship of the ejector module 20 with respect to the first evaporator 17 and the second evaporator 18. Alternatively, or by housing the diffuser portion 52 inside the components of the first evaporator 17 and the second evaporator 18, the ejector-type refrigeration cycle 10 can be downsized as a whole.

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

(1) In each of the above-described embodiments, an example in which the ejector module 20 according to the present invention 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 to this. For example, it may be applied to an ejector-type refrigeration cycle used in a stationary air conditioner, a cold storage cabinet or the like.

(2) In the above-described first embodiment, the ejector module 20 including the variable throttle mechanism 16 and the ejector 15 having the variable nozzle portion has been described. However, the variable throttle mechanism 16 is changed according to the load fluctuation of the ejector refrigeration cycle 10. Further, in order to bring the flow rate of the refrigerant flowing into the nozzle section 51 close to an appropriate flow rate, it is only necessary that at least one of the variable throttle mechanism 16 and the nozzle section 51 has a changeable passage cross-sectional area.

Therefore, as described in the second embodiment, the variable aperture mechanism 16 may be adopted and the ejector 15 having the fixed nozzle portion may be adopted. 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 the ejector 15 having a variable nozzle portion may be employed.

Further, in the above-described embodiment, an example in which the nozzle portion side driving mechanism 54 and the pressure reducing side driving mechanism 62 are configured by mechanical mechanisms has been described, but the nozzle portion side driving mechanism 54 and the pressure reducing side driving mechanism are described. As 62, an electric drive mechanism having an actuator composed of a stepping motor or the like may be adopted.

Further, in the above-described embodiment, an example in which the nozzle portion side central axis CL1 (or the central axis of the nozzle portion 51 ) and the pressure reducing side central axis CL2 are in the twisted positional relationship has been described, but the present invention is not limited to this. The miniaturization effect of accommodating at least a part of the diffuser portion 52 in the collecting pipe 19 or the second evaporator 18 can be obtained even when the nozzle portion side central axis CL1 and the pressure reducing side central axis CL2 are arranged in parallel. You can

Further, in the first embodiment, the example in which the nozzle portion side temperature sensitive portion 54a is arranged in the space communicating with the outflow side passage 20c has been described, but at least a part of the nozzle portion side temperature sensitive portion 54a is disposed in the outflow side passage 20c. You may arrange. Further, an example in which a part of the pressure reducing side drive mechanism 62 is arranged in the suction side passage 20b has been described, but the pressure reducing side drive mechanism 62 may be arranged in a space communicating with the suction side passage 20b.

(3) Each component device that configures the ejector-type refrigeration cycle 10 is not limited to the one disclosed in the above embodiment.

For example, in the above-described embodiment, an example in which an electric compressor is used as the compressor 11 has been described, but the compressor 11 is driven by the rotational driving force transmitted from the vehicle running engine via the pulley, the belt, and the like. An engine driven compressor may be used. Furthermore, as an engine-driven compressor, it is possible to adjust the refrigerant discharge capacity by changing the capacity of the variable capacity compressor that can adjust the refrigerant discharge capacity by changing the discharge capacity, or by changing the operation rate of the compressor by connecting and disconnecting the electromagnetic clutch. Any fixed capacity compressor can be adopted.

In addition, in the above-described embodiment, an example in which a receiver-integrated condenser is adopted as the radiator 12 has been described. However, the radiator 12 further includes a supercooling unit that supercools the liquid-phase refrigerant that has flowed out from the receiver unit 12b. A so-called subcool type condenser configured may be adopted. In addition to this, a radiator 12 including only the condenser 12a and a liquid receiver (receiver) that separates the gas-liquid of the refrigerant that has flowed out from the radiator 12 and causes the separated liquid-phase refrigerant to flow to the downstream side are provided. May be adopted.

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

Further, in the above-described embodiment, an example in which R134a is adopted as the refrigerant has been described, but the refrigerant is not limited to this. For example, R1234yf, R600a, R410A, R404A, R32, R407C, etc. may be adopted. Alternatively, a mixed refrigerant obtained by mixing plural kinds of these refrigerants may be adopted. Furthermore, carbon dioxide may be adopted as the refrigerant to configure a supercritical refrigeration cycle in which the pressure of the high-pressure side refrigerant is equal to or higher than the critical pressure of the refrigerant.

10 Ejector type refrigeration cycle 11 Compressor 12 Radiator,
17 1st evaporator 18 2nd evaporator 20 Ejector module 20a Throttle passage 21 Body part 51 Nozzle part 52 Diffuser part (pressurization part)
200 evaporator unit

Claims (4)

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 the compression that evaporates the refrigerant. An ejector module applied to an ejector-type refrigeration cycle (10) having a second evaporator (18) for flowing out to a suction port side of a machine,
A nozzle part (51) for depressurizing and ejecting a part of the refrigerant flowing out from the radiator,
A decompression unit (20a) for decompressing another part of the refrigerant flowing out from the radiator,
A body portion (21) having a refrigerant suction port (21b) for sucking the refrigerant from the outside by the suction action of the jet refrigerant jetted from the nozzle portion;
A pressurizing unit (52) for pressurizing a mixed refrigerant of the injection refrigerant and the suction refrigerant sucked from the refrigerant suction port,
A pressure reducing valve body (61) for changing the passage cross-sectional area of the pressure reducing portion,
A pressure reducing side drive unit (62) for displacing the pressure reducing side valve body ,
The refrigerant inlet side of the first evaporator is connected to the throttle side outlet (21d) for flowing out the refrigerant from the pressure reducing section,
The 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) that causes the refrigerant to flow out from the pressure booster,
At least the pressure reducing portion of the nozzle portion and the pressure reducing portion is configured to be able to change the passage cross-sectional area,
At least a part of the pressurizing unit is a pipe (19) connected to the inside of at least one of the first evaporator and the second evaporator or to at least one of the first evaporator and the second evaporator. It is arranged so as to be able to be housed inside, protruding from the body portion ,
A suction side passage (20b) through which the refrigerant flowing out of the first evaporator is circulated is formed in the body portion,
The pressure reducing side driving unit has a pressure reducing side temperature sensing unit (62a) having a pressure reducing side deforming member (62b) that deforms according to the temperature and pressure of the refrigerant flowing out from the first evaporator,
An ejector module in which at least a part of the pressure-reducing side temperature-sensing section is arranged in the suction-side passage or in a space communicating with the suction-side passage . A nozzle part valve body part (53) for changing the passage cross-sectional area of the nozzle part;
A nozzle part side drive part (54) for displacing the nozzle part side valve body part,
An outflow side passage (20c) is formed in the body portion to allow the refrigerant flowing out from the second evaporator to flow therethrough,
The nozzle unit side driving unit includes a nozzle unit side temperature sensing unit (54a) having a nozzle unit side deforming member (54b) that deforms according to the temperature and pressure of the refrigerant flowing out from the second evaporator.
The ejector module according to claim 1, wherein at least a part of the temperature sensing portion on the nozzle portion side is arranged in the outflow passage or in a space communicating with the outflow passage. The ejector module according to claim 1 or 2 , wherein the pressure reducing side driving unit displaces the pressure reducing side valve body portion so that the degree of superheat of the first evaporator outlet side refrigerant approaches 0°C. In the body part, a high pressure inlet (21a) into which the refrigerant flowing out from the radiator flows, an outflow side passage (20c) that guides 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 allowing the refrigerant to flow out of the outlet-side passage are formed.
The high pressure inlet and the low pressure outlet are open in the same direction,
The ejector module according to any one of claims 1 to 3 , wherein the ejector-side outlet, the low-pressure inlet, the refrigerant suction port, and the throttle-side outlet are open in the same direction.

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