WO2017179321A1 - Ejector - Google Patents

Abstract

An ejector wherein a passage-forming member (35) formed in a conical shape is arranged inside a body (30) in which an inflow space (30a) for allowing the inflow of a high-pressure refrigerant is formed, thereby forming a nozzle passage (13a) having an annular cross section and functioning as a nozzle, and a diffuser passage (13c) having an annular cross section and functioning as a pressure-boosting part. Furthermore, a shaft (38) extending toward the inflow-space side and slidably supported in the body is coupled to the passage-forming member. The ejector is additionally provided with a pressure-receiving part (38a) which, when the load received by the passage-forming member due to the refrigerant pressure inside the inflow space is defined as a first load (Pw1), receives a second load (Pw2) in a direction cancelling out the first load on the shaft. Thus, it is possible to prevent fluctuations in the first load from influencing displacement of the passage-forming member. Thus, regardless of load fluctuations in a refrigeration cycle device to which the ejector is applied, the passage cross-sectional area of an internally formed refrigerant passage can be changed appropriately.

Description

Ejector Cross-reference of related applications

This application is based on Japanese Patent Application No. 2016-080129 filed on April 13, 2016, the disclosure of which is incorporated herein by reference.

The present disclosure relates to an ejector that decompresses a fluid and sucks the fluid by a suction action of a jet fluid ejected at a high speed.

Conventionally, Patent Document 1 discloses an ejector applied to a vapor compression refrigeration cycle apparatus. With the ejector of this patent document 1, the refrigerant | coolant which flowed out from the evaporator from the refrigerant | coolant suction port formed in the body is attracted | sucked by the suction effect | action of the injection refrigerant | coolant injected from the nozzle channel | path which decompresses a high pressure refrigerant | coolant. Then, in the diffuser passage, the pressure of the mixed refrigerant of the injection refrigerant and the suction refrigerant (that is, the evaporator outlet side refrigerant) is increased and flows out to the suction side of the compressor.

More specifically, in the ejector of Patent Document 1, a passage forming member that is a substantially conical valve body is disposed inside the body, and a cross-sectional circle is formed between the inner wall surface of the body and the conical side surface of the passage forming member. An annular refrigerant passage is formed. Of these refrigerant passages, a portion on the most upstream side of the refrigerant flow is used as a nozzle passage, and a portion on the downstream side of the refrigerant flow in the nozzle passage is used as a diffuser passage.

Furthermore, the ejector of Patent Document 1 includes a drive mechanism that displaces the passage forming member and changes the passage cross-sectional area of the refrigerant passage such as the nozzle passage and the diffuser passage. Thereby, in the ejector of patent document 1, it is going to change the passage cross-sectional area of a refrigerant path according to the load fluctuation | variation of the applied refrigeration cycle apparatus, and to operate an ejector appropriately according to the circulating refrigerant flow rate which circulates through a cycle. Yes.

JP 2013-177879 A

By the way, in an ejector provided with a drive mechanism as in Patent Document 1, it is desirable to employ a small drive mechanism in order to suppress an increase in size of the entire ejector.

However, when a small drive mechanism is employed, the amount of displacement of the passage forming member tends to be small. For this reason, in an ejector employing a small drive mechanism, the refrigerant passage of the body is provided so that a sufficient passage cross-sectional area of the refrigerant passage can be secured even when the heat load of the refrigeration cycle apparatus increases. It is desirable that the opening diameter of the part to be formed (that is, the outer diameter of the refrigerant passage when viewed from the central axis direction) is set to a sufficiently large value in advance.

However, if the opening diameter of the part that forms the refrigerant passage is set to a large value, the area of the part that receives the pressure of the high-pressure refrigerant in the top of the passage forming member becomes large. Therefore, the pressure fluctuation of the high-pressure refrigerant tends to affect the displacement of the passage forming member. For example, when pressure fluctuation occurs in the high-pressure refrigerant, the passage cross-sectional area of the refrigerant passage cannot be adjusted appropriately.

This indication aims at providing the ejector comprised so that the passage cross-sectional area of the refrigerant passage formed inside could be changed appropriately according to the load fluctuation of the applied refrigeration cycle device in view of the above-mentioned point. To do.

According to one aspect of the present disclosure, the ejector is applied to a vapor compression refrigeration cycle apparatus. The ejector includes a body, a passage forming member, a drive mechanism, and a rod-shaped member. The body includes an inflow space into which the high-pressure refrigerant flows, a decompression space to decompress the refrigerant that has flowed out of the inflow space, a suction passage that circulates the refrigerant sucked from the refrigerant suction port in communication with the refrigerant flow downstream side of the decompression space, And a pressure increasing space for allowing the injected refrigerant injected from the pressure reducing space and the suction refrigerant sucked through the suction passage to flow in. The passage forming member is at least partially disposed in the decompression space and in the pressurization space, and is formed in a conical shape whose outer diameter increases as the distance from the decompression space increases. The drive mechanism displaces the passage forming member, and the rod-like member is connected to the passage forming member and extends to the inflow space side and is slidably supported by the body. The refrigerant passage formed between the inner peripheral surface of the part of the body that forms the decompression space and the outer peripheral surface of the passage forming member is a nozzle passage that functions as a nozzle that decompresses and injects the refrigerant. The refrigerant passage formed between the inner peripheral surface of the part of the body that forms the pressurization space and the outer peripheral surface of the passage forming member is a diffuser passage that functions as a booster for mixing and increasing the pressure of the injected refrigerant and the suction refrigerant. It is. When the load that the passage forming member receives from the refrigerant in the inflow space is the first load, the rod-shaped member has a pressure receiving portion that receives the second load in a direction that cancels the first load from the refrigerant in the inflow space. Yes.

According to this, since the rod-shaped member has the pressure receiving part, even if the first load fluctuates due to the load fluctuation of the refrigeration cycle apparatus, the fluctuation can be canceled out by the second load received by the pressure receiving part. . That is, it is possible to reduce the influence of the variation in the first load on the displacement of the passage forming member.

Therefore, it is possible to provide an ejector configured such that the cross-sectional area of the refrigerant passage formed therein can be appropriately changed in accordance with the load fluctuation of the applied refrigeration cycle apparatus.

Further, by setting the pressure receiving area of the pressure receiving portion so that the first load and the second load are equal, even if a pressure fluctuation occurs in the high-pressure refrigerant in the inflow space, the fluctuation is detected in the passage forming member. It is possible to effectively suppress the influence of the displacement.

It is a figure showing an ejector type refrigerating cycle of a 1st embodiment of this indication. It is sectional drawing parallel to the axial direction of the ejector of 1st Embodiment. FIG. 3 is a cross-sectional view taken along the line III-III in FIG. It is a figure which shows the IV section of FIG. It is a Mollier diagram which shows the change of the state of the refrigerant | coolant in the ejector type refrigeration cycle of 1st Embodiment. It is an axial sectional view of an ejector of a 2nd embodiment of this indication. It is a typical expanded sectional view of the VII part of FIG. It is an axial sectional view of an ejector of a 3rd embodiment of this indication. It is a typical expanded sectional view of the IX part of FIG. It is a typical expanded sectional view of the ejector of 4th Embodiment of this indication. It is a typical expanded sectional view of the ejector of a 5th embodiment of this indication.

Hereinafter, a plurality of modes for carrying out the present disclosure will be described with reference to the drawings. In each embodiment, parts corresponding to the matters described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. When only a part of the configuration is described in each mode, the other modes described above can be applied to the other parts of the configuration. Not only combinations of parts that clearly show that combinations are possible in each embodiment, but also combinations of the embodiments even if they are not explicitly stated unless there is a problem with the combination. Is also possible.

(First embodiment)
A first embodiment of the present disclosure will be described with reference to FIGS. 1 to 5. As shown in FIG. 1, the ejector 13 of the present embodiment is applied to a vapor compression refrigeration cycle apparatus including an ejector as a refrigerant decompression apparatus, that is, an ejector refrigeration cycle 10. Furthermore, this ejector type refrigeration cycle 10 is applied to a vehicle air conditioner, and fulfills a function of cooling the blown air blown into the vehicle interior, which is the air-conditioning target space. Therefore, the cooling target fluid of the ejector refrigeration cycle 10 of the present embodiment is blown air.

Further, the ejector refrigeration cycle 10 of the present embodiment employs an HFO refrigerant (specifically, R1234yf) as the refrigerant, and constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant. is doing. This refrigerant is mixed with refrigerating machine oil for lubricating the compressor 11, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.

Of the constituent devices of the ejector refrigeration cycle 10, the compressor 11 sucks refrigerant and discharges it until it becomes high-pressure refrigerant. The compressor 11 is disposed in an engine room together with an engine (internal combustion engine) that outputs a driving force for vehicle travel. Further, the compressor 11 is an engine-driven compressor that is driven by a rotational driving force output from the engine via a pulley, a belt, or the like.

More specifically, in the present embodiment, a swash plate type variable displacement compressor configured such that the refrigerant discharge capacity can be adjusted by changing the discharge capacity is adopted as the compressor 11. The compressor 11 has a discharge capacity control valve (not shown) for changing the discharge capacity. The operation of the discharge capacity control valve is controlled by a control current output from a control device described later.

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 exchanger for heat radiation 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 by the cooling fan 12d. . The radiator 12 is arranged on the vehicle front side in the engine room.

More specifically, the radiator 12 is configured as a so-called subcool type condenser having a condensing unit 12a, a receiver unit 12b, and a supercooling unit 12c.

The condensing unit 12a is a heat exchange 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 12d, 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 supercooling unit 12c is a heat exchange unit for supercooling that causes the liquid phase refrigerant that has flowed out of the receiver unit 12b and the outside air blown from the cooling fan 12d to exchange heat, thereby supercooling the liquid phase refrigerant.

The cooling fan 12d is an electric blower in which the rotation speed (that is, the amount of blown air) is controlled by a control voltage output from the control device. A refrigerant inlet 31 a of the ejector 13 is connected to the refrigerant outlet side of the supercooling portion 12 c of the radiator 12.

The ejector 13 functions as a refrigerant decompression device that decompresses the supercooled high-pressure liquid-phase refrigerant that has flowed out of the radiator 12 and flows it downstream. Further, the ejector 13 has a function as a refrigerant transporting device that sucks and transports a refrigerant (that is, an outlet side refrigerant of the evaporator 14) that flows out from the evaporator 14 (described later) by the suction action of the jetted refrigerant that is injected at a high speed. Fulfill.

In addition to this, the ejector 13 of the present embodiment also has a function of a gas-liquid separator that separates the gas-liquid of the decompressed refrigerant. In other words, the ejector 13 of the present embodiment is configured as an ejector with a gas-liquid separation function in which the ejector and the gas-liquid separator are integrated (that is, modularized). The ejector 13 is disposed in the engine room together with the compressor 11 and the radiator 12.

The specific configuration of the ejector 13 will be described with reference to FIGS. 2 and 3 are axial sectional views of the ejector 13, FIG. 2 is a sectional view taken along the line II-II in FIG. 3, and FIG. 3 is a sectional view taken along the line III-III in FIG. Moreover, the up and down arrows in FIG. 3 indicate the up and down directions in a state where the ejector refrigeration cycle 10 is mounted on the vehicle air conditioner.

The ejector 13 of the present embodiment includes a body 30 formed by combining a plurality of constituent members as shown in FIGS.

More specifically, the body 30 includes an upper body 311, a lower body 312, a gas-liquid separation body 313, and the like. The upper body 311, the lower body 312, and the gas-liquid separation body 313 form an outer shell of the ejector 13 and also function as a housing that accommodates other components inside.

The upper body 311, the lower body 312, and the gas-liquid separation body 313 are formed of hollow members made of metal (in this embodiment, made of an aluminum alloy). The upper body 311, the lower body 312 and the gas-liquid separation body 313 may be formed of resin.

In the internal space formed by combining the upper body 311 and the lower body 312, constituent members of the body 30 such as a nozzle body 32 and a diffuser body 33 described later are fixed.

The upper body 311 is formed with a plurality of refrigerant inlets such as a refrigerant inlet 31a and a refrigerant suction port 31b. The refrigerant inlet 31 a is a refrigerant inlet through which the high-pressure refrigerant that has flowed out of the radiator 12 flows. The refrigerant suction port 31b is a refrigerant inflow port that sucks the low-pressure refrigerant that has flowed out of the evaporator 14.

The gas-liquid separation body 313 is formed with a plurality of refrigerant outlets such as a liquid-phase refrigerant outlet 31c and a gas-phase refrigerant outlet 31d. The liquid-phase refrigerant outlet 31 c is a refrigerant outlet that allows the liquid-phase refrigerant separated in the gas-liquid separation space 30 f formed in the gas-liquid separation body 313 to flow out to the refrigerant inlet side of the evaporator 14. The gas-phase refrigerant outlet 31d is a refrigerant outlet through which the gas-phase refrigerant separated in the gas-liquid separation space 30f flows out to the suction port side of the compressor 11.

The nozzle body 32 is formed of a cylindrical member made of metal (in this embodiment, stainless steel). As shown in FIGS. 2 and 3, the nozzle body 32 is disposed on the bottom surface of the upper body 311 on the lower body 312 side. The nozzle body 32 is fixed by press-fitting into a hole formed in the upper body 311, and the refrigerant does not leak from the gap between the upper body 311 and the nozzle body 32.

In the nozzle body 32, an inflow space 30a for allowing the refrigerant that has flowed in from the refrigerant inflow port 31a to flow is formed. The inflow space 30a is formed in a substantially cylindrical rotating body shape. A central axis of the inflow space 30a is arranged coaxially with a central axis CL of a passage forming member 35 described later. Further, as is clear from FIGS. 2 and 3, the central axis CL of the present embodiment extends in a substantially horizontal direction. The rotating body shape is a three-dimensional shape formed when a plane figure is rotated around one straight line (center axis) on the same plane.

The upper body 311 is formed with a refrigerant inflow passage 31e that guides the high-pressure refrigerant that has flowed from the refrigerant inlet 31a into the inflow space 30a. The refrigerant inflow passage 31e is formed in a shape extending in the radial direction when viewed from the central axis direction of the inflow space 30a, and causes the refrigerant flowing into the inflow space 30a to flow toward the central axis of the inflow space 30a. Is formed.

A decompression space that is formed inside the nozzle body 32 downstream of the refrigerant flow in the inflow space 30a so as to be continuous with the inflow space 30a and depressurizes the refrigerant that has flowed out of the inflow space 30a and flows out downstream. 30b is formed.

The decompression space 30b is formed in a rotating body shape in which the top sides of two frustoconical spaces are joined together. The central axis of the decompression space 30b is also arranged coaxially with the central axis CL of the passage forming member 35. In the decompression space 30b, a minimum passage area portion 30m that reduces the passage sectional area of the decompression space 30b (specifically, a nozzle passage 13a described later) is formed.

In the decompression space 30b, the top side of the passage forming member 35 formed in a conical shape is disposed. The passage forming member 35 is a valve body portion that changes the passage cross-sectional area of the refrigerant passage formed inside the ejector 13 by being displaced in the direction of the central axis CL.

The passage forming member 35 is formed in a conical shape in which the outer diameter increases as the distance from the decompression space 30b increases (that is, toward the downstream side of the refrigerant flow). For this reason, a refrigerant passage in which the shape of the vertical cross section in the axial direction is annular between the inner peripheral surface of the portion forming the pressure reducing space 30b of the nozzle body 32 and the outer peripheral surface of the portion on the top side of the passage forming member 35. Is formed. The detailed configuration of the passage forming member 35 will be described later.

This refrigerant passage is a nozzle passage 13a that functions as a nozzle for depressurizing and injecting refrigerant in an isentropic manner. In the nozzle passage 13a, the passage sectional area decreases from the inflow space 30a side toward the minimum passage area portion 30m, and the passage sectional area increases again from the minimum passage area portion 30m toward the refrigerant flow downstream side. That is, in the nozzle passage 13a, the passage cross-sectional area changes like a so-called Laval nozzle.

Thereby, in the nozzle passage 13a of the present embodiment, the refrigerant can be decompressed and injected while increasing the flow velocity of the refrigerant to be supersonic.

The diffuser body 33 is disposed inside the upper body 311 and on the downstream side of the refrigerant flow with respect to the nozzle body 32. The diffuser body 33 is formed of a cylindrical member made of metal (in this embodiment, aluminum alloy).

The diffuser body 33 is fixed to the upper body 311 by press-fitting the outer peripheral side thereof to the inner peripheral side surface of the upper body 311. An O-ring (not shown) is arranged between the outer peripheral surface of the diffuser body 33 and the inner peripheral surface of the upper body 311 so that the refrigerant does not leak from the gap between these members.

At the center of the diffuser body 33, a through hole 33a penetrating in the axial direction is formed. The central axis of the through hole 33 a is arranged coaxially with the central axis of the passage forming member 35. The through-hole 33a is formed in a substantially truncated cone shape whose cross-sectional area increases toward the downstream side of the refrigerant flow. Furthermore, in the present embodiment, the tip of the nozzle body 32 on the refrigerant injection port side extends to the inside of the through hole 33 a of the diffuser body 33.

Then, between the inner peripheral surface of the through-hole 33a of the diffuser body 33 and the outer peripheral surface of the cylindrical tip portion of the nozzle body 32, the refrigerant sucked from the refrigerant suction port 31b is reduced in the pressure reducing space 30b (that is, the nozzle passage). 13a) is formed a suction passage 13b for guiding the refrigerant flow downstream. For this reason, when viewed from the direction of the central axis CL, the suction refrigerant outlet serving as the most downstream portion of the suction passage 13b opens in an annular shape on the outer peripheral side of the refrigerant injection port.

In the through hole 33a of the diffuser body 33, on the downstream side of the refrigerant flow in the suction passage 13b, a pressure increasing space 30e formed in a substantially truncated cone shape gradually spreading in the refrigerant flow direction is formed. The pressurizing space 30e is a space into which the injection refrigerant injected from the nozzle passage 13a and the suction refrigerant sucked from the suction passage 13b flow.

In the pressurizing space 30e, the refrigerant flow downstream side of the top of the passage forming member 35 is disposed. Between the inner peripheral surface of the diffuser body 33 forming the pressurizing space 30e and the outer peripheral surface of the passage forming member 35 on the downstream side of the refrigerant flow, a refrigerant passage having an annular shape in the axial vertical cross section is formed. Is done.

This refrigerant passage is a diffuser passage 13c that functions as a boosting unit that boosts the pressure by mixing the injected refrigerant and the suction refrigerant. In the diffuser passage 13c, the passage cross-sectional area is gradually enlarged toward the downstream side of the refrigerant flow. Thereby, in the diffuser channel | path 13c, the velocity energy of the mixed refrigerant | coolant of an injection refrigerant | coolant and a suction | inhalation refrigerant | coolant can be converted into pressure energy.

Next, the detailed configuration of the passage forming member 35 will be described. The passage forming member 35 is formed of a conical member made of a resin (in this embodiment, made of nylon 6 or nylon 66) having resistance to the refrigerant. A substantially frustoconical space is formed inside the passage forming member 35 from the bottom surface side. That is, the passage forming member 35 is formed in a cup shape (that is, a cup shape).

A shaft 38 is connected to the passage forming member 35. The shaft 38 is a rod-shaped member formed of a columnar metal (in this embodiment, stainless steel). The central axis of the shaft 38 is arranged coaxially with the central axis CL of the passage forming member 35. The shaft 38 is insert-molded in the passage forming member 35. Thereby, the channel | path formation member 35 and the shaft 38 are integrated.

One end side (inflow space 30a side) of the shaft 38 protrudes from the top of the passage forming member 35 and extends toward the inflow space 30a, and is slidably supported by the upper body 311. The other end side of the shaft 38 extends toward the bottom surface side of the passage forming member 35 and is slidably supported by a bearing hole of the support member 36 fixed to the lower body 312. Accordingly, the shaft 38 is slidably supported by the body 30 at both ends in the central axis direction.

2 and 3, the support member 36 is formed of a metal (aluminum alloy in this embodiment) cylindrical member, and is fixed to the lower body 312 via a fixing member (not shown).

Furthermore, a coil spring 36a for applying a load that biases the shaft 38 toward the inflow space 30a (side to reduce the passage cross-sectional area of the nozzle passage 13a) is accommodated inside the support member 36. The load of the coil spring 36 a can be adjusted by an adjustment screw 36 b provided on the support member 36.

Further, a pressure receiving portion 38 a that receives the pressure of the refrigerant in the inflow space 30 a is formed on one end side of the shaft 38. The pressure receiving part 38a is a part formed in a columnar shape by enlarging the outer diameter of the shaft 38 more than other parts. The upper body 311 is formed with a cylindrical space into which the pressure receiving portion 38a is fitted.

Here, as described above, the top side of the passage forming member 35 is disposed in a decompression space 30b formed so as to be continuous with the inflow space 30a in the nozzle body 32. For this reason, the top side of the passage forming member 35 receives the first load Pw1 generated by the pressure of the high-pressure refrigerant in the inflow space 30a as shown by the thick solid arrows in FIGS. The first load Pw1 is a load that biases the passage forming member 35 toward the side of enlarging the passage sectional area in the minimum passage area 30m.

On the other hand, the pressure receiving portion 38a receives the second load Pw2 generated by the pressure of the high-pressure refrigerant in the inflow space 30a as shown by the thick solid arrows in FIGS. The second load Pw2 is a load that biases the pressure receiving portion 38a connected to the passage forming member 35 toward the side that reduces the passage sectional area in the minimum passage area 30m. That is, the second load Pw2 is a load in a direction that cancels out the first load Pw1.

Therefore, the pressure receiving area of the pressure receiving portion 38a of the present embodiment is set so that the first load Pw1 and the second load Pw2 are equal. More specifically, when viewed from the direction of the central axis CL, the pressure receiving area of the portion on the top side of the passage forming member 35 that receives the pressure of the high pressure refrigerant in the inflow space 30a, and the pressure of the high pressure refrigerant in the pressure receiving portion 38a The pressure receiving area of the annular portion that receives the pressure is set to be equal.

In addition, the 1st load Pw1 and the 2nd load Pw2 being equal does not only mean that the 1st load Pw1 and the 2nd load Pw2 correspond completely. This means that the load difference Pw1−Pw2 between the first load Pw1 and the second load Pw2 includes a range that is small enough not to affect the drive mechanism 37 described later when the passage forming member 35 is displaced.

Further, as shown in FIG. 4, a flat plate sealing member 381 is disposed on the end face of one end side of the pressure receiving portion 38a (the opposite side of the inflow space 30a, that is, the drive mechanism 37 side). The flat seal member 381 is a seal that prevents high-pressure refrigerant in the inflow space 30a from flowing out of the inflow space 30a through a gap between the upper body 311 and the shaft 38 (specifically, the pressure receiving portion 38a). It is a member.

The flat plate seal member 381 is formed of an annular plate member made of synthetic rubber (EPDM: ethylene propylene diene copolymer rubber in this embodiment). The inner peripheral side of the flat plate sealing member 381 is fixed to the shaft 38, and the outer peripheral side of the flat plate sealing member 381 is fixed to the upper body 311.

More specifically, the inner peripheral side of the flat plate sealing member 381 is fixed between a surface on one end side of the pressure receiving portion 38a and the shaft side pressing member 381a. The shaft-side pressing member 381a is a metal cylindrical member having an outer diameter equivalent to that of the pressure receiving portion 38a. The shaft-side pressing member 381a is press-fitted from one end side of the shaft 38, and is fixed to the shaft 38 in a state where the inner peripheral side of the flat plate sealing member 381 is sandwiched between the one end-side surface of the pressure receiving portion 38a. .

The outer peripheral side of the flat plate sealing member 381 is fixed between a step portion 311a formed on the upper body 311 and the body side pressing member 381b. The body side pressing member 381b is a metal cylindrical member having an outer diameter equivalent to that of the flat plate sealing member 381. The step portion 311a is formed in an annular shape so that the end portion on the other end side of the body side pressing member 381b comes into contact therewith.

The body side pressing member 381b is press-fitted from one end side of the shaft 38, and is fixed to the upper body 311 with the outer peripheral side of the flat plate sealing member 381 sandwiched between the stepped portion 311a.

A gap is formed between the outer peripheral surface of the pressure receiving portion 38a and the inner peripheral surface of the cylindrical space of the upper body 311 as shown in FIG. Accordingly, the shaft 38 can be displaced in the axial direction by bending (deforming) the flat plate sealing member 381. In the present embodiment, the gap dimension δ is set so that the lift amount (axial displacement amount) of the passage forming member 35 can secure the lift amount necessary for appropriately changing the passage sectional area of the refrigerant passage. Yes.

Further, as shown in FIGS. 2 and 3, the tip portion of one end side of the shaft 38 is formed with an outer diameter thinner than the pressure receiving portion 38a. A tip portion on one end side of the shaft 38 is connected to the drive mechanism 37.

The driving mechanism 37 outputs a driving force for displacing the shaft 38 and the passage forming member 35 in the axial direction. In other words, the drive mechanism 37 changes the refrigerant passage cross-sectional area such as the minimum passage area portion 30m of the nozzle passage 13a by displacing the passage forming member 35.

More specifically, as shown in FIGS. 2 and 3, the drive mechanism 37 is disposed outside the upper body 311 and on an extension line in the central axis direction of the shaft 38. The drive mechanism 37 includes a diaphragm 371, an upper cover 372, a lower cover 373, and the like.

The upper cover 372 is a sealed space forming member that forms a part of the sealed space 37a together with the diaphragm 371. The upper cover 372 is a cup-shaped member formed of metal (in this embodiment, stainless steel).

The enclosed space 37a is a space in which a temperature-sensitive medium whose pressure changes with temperature change is enclosed. More specifically, the enclosed space 37a is a space in which a temperature-sensitive medium having the same composition as the refrigerant circulating in the ejector refrigeration cycle 10 is enclosed so as to have a predetermined enclosure density.

Therefore, a medium mainly composed of R1234yf (for example, a mixed medium of R1234yf and helium) can be employed as the temperature sensitive medium of the present embodiment. Further, the density of the temperature sensitive medium is set so that the passage forming member 35 can be appropriately displaced during the normal operation of the cycle, as will be described later.

The lower cover 373 is an introduction space forming member that forms the introduction space 37b together with the diaphragm 371. The lower cover 373 is formed of the same metal member as the upper cover 372. The introduction space 37b is a space for introducing the suction refrigerant sucked from the refrigerant suction port 31b through the communication path 311b.

The outer peripheral edges of the upper cover 372 and the lower cover 373 are fixed by caulking or the like. Further, the outer peripheral side portion of the diaphragm 371 is sandwiched between the upper cover 372 and the lower cover 373. Thereby, the diaphragm 371 partitions the space formed between the upper cover 372 and the lower cover 373 into an enclosed space 37a and an introduction space 37b.

The diaphragm 371 is a pressure responsive member that is displaced according to the pressure difference between the internal pressure of the enclosed space 37a and the pressure of the suction refrigerant flowing through the suction passage 13b. Accordingly, it is desirable that the diaphragm 371 is made of a material that is rich in elasticity and excellent in pressure resistance and airtightness. As such a diaphragm 371, a thin metal plate made of stainless steel (SUS304), a thin plate member made of EPDM with a base fabric, or the like can be used.

A disk-shaped plate member 374 made of metal (in this embodiment, an aluminum alloy) is disposed on the introduction space 37b side of the diaphragm 371 so as to come into contact therewith. Further, the tip of the shaft 38 is connected to the plate member 374. Accordingly, the shaft 38 and the passage forming member 35 of the present embodiment are displaced so that the total load of the load received from the drive mechanism 37 (specifically, the diaphragm 371) and the load received from the coil spring 36a is balanced.

More specifically, when the temperature of the refrigerant on the outlet side of the evaporator 14 (superheat degree SH) rises, the saturation pressure of the temperature sensitive medium enclosed in the enclosed space 37a rises, and the introduction space 37b from the internal pressure in the enclosed space 37a. The pressure difference obtained by subtracting the internal pressure increases. Accordingly, the diaphragm 371 is displaced toward the introduction space 37b, and the load that the shaft 38 receives from the drive mechanism 37 increases.

Therefore, when the temperature of the refrigerant on the outlet side of the evaporator 14 (superheat degree SH) rises, the passage forming member 35 is displaced in a direction in which the passage sectional area in the minimum passage area portion 30m is enlarged.

On the other hand, when the temperature of the refrigerant on the outlet side of the evaporator 14 (superheat degree SH) decreases, the saturation pressure of the temperature sensitive medium enclosed in the enclosed space 37a decreases, and the internal pressure in the introduction space 37b is reduced from the internal pressure in the enclosed space 37a. The subtracted pressure difference becomes smaller. As a result, the diaphragm 371 is displaced toward the enclosed space 37a, and the load that the shaft 38 receives from the drive mechanism 37 is reduced.

Therefore, when the temperature of the refrigerant on the outlet side of the evaporator 14 (superheat degree SH) is lowered, the passage forming member 35 is displaced in a direction of reducing the passage cross-sectional area in the minimum passage area portion 30m.

That is, the drive mechanism 37 of the present embodiment is configured by a mechanical mechanism, and the diaphragm 371 displaces the passage forming member 35 according to the superheat degree SH of the evaporator 14 outlet side refrigerant. The passage cross-sectional area in the minimum passage area portion 30m is adjusted so that the superheat degree SH of the side refrigerant approaches a predetermined reference superheat degree KSH.

The reference superheat KSH can be changed by adjusting the load of the coil spring 36a with the adjusting screw 36b.

Furthermore, in this embodiment, a cover member 375 that covers the drive mechanism 37 is disposed on the outer peripheral side of the drive mechanism 37. Thereby, it is suppressed that the temperature-sensitive medium in the enclosed space 37a is affected by the outside air temperature in the engine room.

Next, as shown in FIGS. 2 and 3, a mixed refrigerant outlet 31 g is formed on the downstream side of the refrigerant flow of the lower body 312. The mixed refrigerant outlet 31g is a refrigerant outlet through which the gas-liquid mixed refrigerant flowing out of the diffuser passage 13c flows out to the gas-liquid separation space 31f formed in the gas-liquid separation body 313. The passage sectional area of the mixed refrigerant outlet 31g is formed smaller than the passage sectional area of the most downstream portion of the diffuser passage 13c.

The gas-liquid separation body 313 is formed in a cylindrical shape. A gas-liquid separation space 30 f is formed inside the gas-liquid separation body 313. The gas-liquid separation space 30f is formed as a substantially cylindrical rotating body-shaped space. The central axes of the gas-liquid separation body 313 and the gas-liquid separation space 30f extend in the vertical direction. For this reason, the gas-liquid separation body 313, the gas-liquid separation space 30f, and the central axis are orthogonal to the central axis CL of the passage forming member 35.

Further, the gas-liquid separation body 313 is arranged so that the refrigerant that has flowed into the gas-liquid separation space 30f from the mixed refrigerant outlet 31g of the lower body 312 flows along the outer peripheral wall surface of the gas-liquid separation space 30f. Yes. Thereby, in the gas-liquid separation space 30f, the gas-liquid of the refrigerant is separated by the action of the centrifugal force generated by the refrigerant turning around the central axis.

At the axial center of the gas-liquid separation body 313, there is provided a cylindrical pipe 313a that is arranged coaxially with the gas-liquid separation space 30f and extends in the vertical direction. A liquid-phase refrigerant outlet through which the liquid-phase refrigerant separated in the gas-liquid separation space 30f flows out along the outer peripheral side wall surface of the gas-liquid separation space 30f is formed on the cylindrical side surface on the bottom side of the gas-liquid separation body 313. 31c is formed. Further, a gas-phase refrigerant outlet 31d through which the gas-phase refrigerant separated in the gas-liquid separation space 30f flows out is formed at the lower end of the pipe 313a.

In addition, a gas-phase refrigerant passage formed in the gas-liquid separation space 30f and the pipe 313a is formed at the root of the pipe 313a in the gas-liquid separation space 30f (that is, the lowermost portion in the gas-liquid separation space 30f). An oil return hole 313b is formed. The oil return hole 313b is a communication path for returning the refrigeration oil dissolved in the liquid phase refrigerant into the compressor 11 through the gas phase refrigerant path together with the liquid phase refrigerant.

As shown in FIG. 1, the refrigerant inlet side of the evaporator 14 is connected to the liquid phase refrigerant outlet 31 c of the ejector 13. The evaporator 14 performs heat exchange between the low-pressure refrigerant decompressed by the ejector 13 and the blown air blown into the vehicle interior from the blower fan 14a, thereby evaporating the low-pressure refrigerant and exerting an endothermic effect. It is a vessel.

The blower fan 14a is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the control device. A refrigerant suction port 31 b of the ejector 13 is connected to the outlet side of the evaporator 14. Further, the suction port side of the compressor 11 is connected to the gas-phase refrigerant outlet 31 d of the ejector 13.

Next, a control device (not shown) includes a known microcomputer including a CPU, a ROM, a RAM, and the like and its peripheral circuits. This control device performs various calculations and processes based on a control program stored in the ROM. Then, the operation of the above-described various electric actuators 11, 12d, 14a and the like is controlled.

In addition, a plurality of air conditioning control sensor groups such as an inside air temperature sensor, an outside air temperature sensor, a solar radiation sensor, an evaporator temperature sensor, and a discharge pressure sensor are connected to the control device, and detection values of these sensor groups are input. The

More specifically, the inside air temperature sensor is an inside air temperature detecting unit that detects the temperature inside the vehicle. The outside air temperature sensor is an outside air temperature detecting unit that detects the outside air temperature. A solar radiation sensor is a solar radiation amount detection part which detects the solar radiation amount in a vehicle interior. The evaporator temperature sensor is an evaporator temperature detector that detects the temperature of the blown air (evaporator temperature) of the evaporator 14. The discharge pressure sensor is an outlet-side pressure detection unit that detects the pressure of the radiator 12 outlet-side refrigerant.

Furthermore, an operation panel (not shown) disposed near the instrument panel in the front part of the vehicle interior is connected to the input side of the control device, and operation signals from various operation switches provided on the operation panel are input to the control device. The As various operation switches provided on the operation panel, there are provided an air conditioning operation switch for requesting air conditioning in the vehicle interior, a vehicle interior temperature setting switch for setting the vehicle interior temperature, and the like.

Note that the control device of the present embodiment is configured integrally with a control unit that controls the operation of various control target devices connected to the output side of the control device. The configuration (hardware and software) for controlling the operation constitutes a dedicated control unit for each control target device.

For example, in the present embodiment, the configuration for controlling the refrigerant discharge capacity of the compressor 11 by controlling the operation of the discharge capacity control valve of the compressor 11 constitutes the discharge capacity control unit. Of course, you may comprise a discharge capability control part with a separate control apparatus with respect to a control apparatus.

Next, the operation of the present embodiment in the above configuration will be described using the Mollier diagram of FIG. First, when the operation switch of the operation panel is turned on (ON), the control device operates the discharge capacity control valve of the compressor 11, the cooling fan 12d, the blower fan 14a, and the like. Thereby, the compressor 11 sucks the refrigerant, compresses it, and discharges it. At this time, the control device increases the refrigerant discharge capacity of the compressor 11 as the heat load of the ejector refrigeration cycle 10 increases.

The high-temperature and high-pressure refrigerant discharged from the compressor 11 (point a in FIG. 5) flows into the condenser 12a of the radiator 12, exchanges heat with the outside air blown from the cooling fan 12d, and dissipates heat to condense. The refrigerant condensed in the condensing unit 12a is gas-liquid separated in the receiver unit 12b. The liquid phase refrigerant separated from the gas and liquid by the receiver unit 12b exchanges heat with the outside air blown from the cooling fan 12d by the supercooling unit 12c, and further dissipates heat to become a supercooled liquid phase refrigerant (a in FIG. 5). Point → b).

The supercooled liquid-phase refrigerant that has flowed out of the supercooling portion 12c of the radiator 12 passes through the nozzle passage 13a formed between the inner peripheral surface of the decompression space 30b of the ejector 13 and the outer peripheral surface of the passage forming member 35. The pressure is reduced entropically and injected (point b → point c in FIG. 5). At this time, the passage cross-sectional area in the minimum passage area 30m of the decompression space 30b is adjusted so that the superheat degree of the evaporator 14 outlet side refrigerant (point h in FIG. 5) approaches the reference superheat degree KSH.

Furthermore, the refrigerant flowing out of the evaporator 14 (point h in FIG. 5) is sucked through the refrigerant suction port 31b and the suction passage 13b by the suction action of the injection refrigerant injected from the nozzle passage 13a. The injection refrigerant injected from the nozzle passage 13a and the suction refrigerant sucked through the suction passage 13b flow into the diffuser passage 13c and join (point c → d point, h1 point → d point in FIG. 5).

Here, the most downstream portion of the suction passage 13b of the present embodiment is formed in a shape in which the passage cross-sectional area gradually decreases in the refrigerant flow direction. For this reason, the suction refrigerant passing through the suction passage 13b increases the flow velocity while decreasing the pressure (point h → point h1 in FIG. 5). Thereby, the speed difference between the suction refrigerant and the injection refrigerant is reduced, and the energy loss (mixing loss) when the suction refrigerant and the injection refrigerant are mixed in the diffuser passage 13c is reduced.

In the diffuser passage 13c, the kinetic energy of the refrigerant is converted into pressure energy by expanding the passage cross-sectional area. As a result, the pressure of the mixed refrigerant rises while the injected refrigerant and the suction refrigerant are mixed (point d → point e in FIG. 5). The refrigerant flowing out of the diffuser passage 13c is gas-liquid separated in the gas-liquid separation space 30f (e point → f point, e point → g point in FIG. 5).

The liquid-phase refrigerant separated in the gas-liquid separation space 30f flows into the evaporator 14 with pressure loss when flowing through the refrigerant flow path from the ejector 13 to the evaporator 14 (g point → g1 in FIG. 5). point). The refrigerant flowing into the evaporator 14 absorbs heat from the blown air blown by the blower fan 14a and evaporates (g1 point → h point in FIG. 5). Thereby, blowing air is cooled.

On the other hand, the gas-phase refrigerant separated in the gas-liquid separation space 30f flows out of the gas-phase refrigerant outlet 31d, is sucked into the compressor 11, and is compressed again (point f → a in FIG. 5).

The ejector refrigeration cycle 10 of the present embodiment operates as described above, and can cool the blown air blown into the vehicle interior.

In the ejector refrigeration cycle 10 of the present embodiment, the refrigerant whose pressure has been increased in the diffuser passage 13c is sucked into the compressor 11. Therefore, according to the ejector-type refrigeration cycle 10, the power consumption of the compressor 11 can be reduced compared with the normal refrigeration cycle apparatus in which the refrigerant evaporation pressure in the evaporator and the pressure of the refrigerant sucked by the compressor are substantially equal. Coefficient of performance (COP) can be improved.

Further, since the ejector 13 of the present embodiment includes the drive mechanism 37, the passage forming member 35 is displaced in accordance with the load fluctuation of the ejector refrigeration cycle 10, and the passage sectional area (minimum passage area) of the nozzle passage 13a is displaced. The cross-sectional area of the portion 30m) and the cross-sectional area of the diffuser passage 13c can be adjusted.

Thereby, according to the load fluctuation | variation of the ejector-type refrigeration cycle 10, the passage sectional area of the refrigerant passage (specifically, the nozzle passage 13a and the diffuser passage 13c) formed inside is changed, and the ejector-type refrigeration cycle The ejector 13 can be appropriately operated in accordance with the flow rate of the circulating refrigerant circulating in 10.

At this time, in the ejector 13 of the present embodiment, the passage forming member 35 and the shaft 38 are integrated, and the shaft 38 is supported at both ends of the central axis CL.

Therefore, even if the drive mechanism 37 displaces the passage forming member 35, the central axis CL of the passage forming member 35 is prevented from being inclined with respect to the central axes of the decompression space 30b, the boosting space 30e, and the like. Can do. As a result, it is possible to prevent the ejector efficiency from becoming unstable due to the central axis CL of the passage forming member 35 being inclined.

Further, since the pressure receiving portion 38a is formed on the shaft 38 of the ejector 13 of the present embodiment, the pressure fluctuation of the high-pressure refrigerant flowing into the inflow space 30a occurs due to the load fluctuation of the ejector refrigeration cycle 10, and the first Even if one load Pw1 fluctuates, this variation can be canceled out by the second load Pw2 received by the pressure receiving portion 38a. That is, the influence of the fluctuation of the first load Pw1 on the displacement of the passage forming member 35 can be reduced.

In addition, in this embodiment, the pressure receiving area of the pressure receiving portion 38a is set so that the first load Pw1 and the second load Pw2 are equal. Thereby, even if a pressure fluctuation occurs in the high-pressure refrigerant flowing into the inflow space 30a, it is possible to effectively suppress the fluctuation from adversely affecting the displacement of the passage forming member 35.

Therefore, according to the ejector 13 of the present embodiment, the passage cross-sectional areas of the nozzle passage 13a and the diffuser passage 13c can be appropriately changed according to the load fluctuation of the applied ejector refrigeration cycle 10.

In addition, since the ejector 13 according to the present embodiment includes the flat plate sealing member 381, the high-pressure refrigerant in the inflow space 30a is prevented from flowing out through the gap between the upper body 311 and the shaft 38. Can do.

Furthermore, the flat plate sealing member 381 is formed of an annular plate-like member, and the inner peripheral side is fixed to the shaft 38 and the outer peripheral side is fixed to the upper body 311. According to this, a gap can be formed between the outer peripheral surface of the pressure receiving portion 38 a and the inner peripheral surface of the upper body 311.

Therefore, the passage forming member 35 connected to the shaft 38 can be displaced without increasing the sliding resistance between the shaft 38 and the upper body 311. As a result, when the passage forming member 35 is displaced, it is possible to suppress the deterioration of responsiveness and the increase of hysteresis.

Further, by appropriately setting the gap dimension δ between the outer peripheral surface of the pressure receiving portion 38 a and the inner peripheral surface of the upper body 311, the lift of the passage forming member 35 necessary for appropriately changing the passage cross-sectional area of the refrigerant passage. A certain amount can be ensured.

In the ejector 13 of the present embodiment, the refrigerant inflow passage 31e causes the refrigerant flowing into the inflow space 30a to flow toward the central axis of the inflow space 30a when viewed from the central axis direction of the inflow space 30a. Is formed.

Further, rigid bodies such as a shaft 38 and a passage forming member 35 are disposed in the center of the inflow space 30a, the pressure reducing space 30b, and the pressure increasing space 30e. Accordingly, the axial vertical cross-sectional shapes of all the refrigerant passages formed by the inflow space 30a, the decompression space 30b, and the pressurization space 30e are annular. According to this, it is possible to suppress the swirling flow around the central axis from occurring in the refrigerant in the inflow space 30a.

Therefore, an increase in mixing loss when mixing the injected refrigerant and the suction refrigerant can be suppressed, and the ejector efficiency can be improved. This is particularly effective in the ejector 13 in which the suction refrigerant outlet 13f of the suction passage 13b is annularly opened on the outer peripheral side of the refrigerant injection port 13e of the nozzle passage 13a, like the ejector 13 of the present embodiment.

Further, in the ejector 13 of the present embodiment, the passage sectional area of the mixed refrigerant outlet 31g is formed to be smaller than the passage sectional area of the most downstream portion of the diffuser passage 13c, and further the gas-liquid mixture flowing out of the diffuser passage 13c The refrigerant in the state is caused to flow along the outer peripheral wall surface of the gas-liquid separation space 30f. According to this, the pressure loss of the refrigerant generated in the gas-liquid separation space 30f can be reduced.

This will be described in more detail. At the mixed refrigerant outlet 31g, the static pressure of the refrigerant decreases due to the reduction of the passage cross-sectional area, but the refrigerant flowing into the gas-liquid separation space 30f from the mixed refrigerant outlet 31g It flows along the inner peripheral wall surface of the liquid separation body 313 (that is, the outer peripheral wall surface of the gas-liquid separation space 30f).

For this reason, since the vapor phase refrigerant flowing into the gas-liquid separation space 30f from the mixed refrigerant outlet 31g is suppressed from rapidly expanding when it flows into the gas-liquid separation space 30f, energy loss due to volume expansion is reduced. Can be suppressed. On the other hand, with respect to the liquid-phase refrigerant flowing into the gas-liquid separation space 30f from the mixed refrigerant outlet 31g, energy loss occurs only for the wall friction that has relatively little influence.

Therefore, the kinetic energy of the refrigerant that has flowed into the gas-liquid separation space 30f having a relatively large volume from the mixed refrigerant outlet 31g is converted into pressure energy without loss, and the static pressure of the refrigerant is restored. Thereby, the pressure loss of the refrigerant | coolant produced in the gas-liquid separation space 30f can be reduced.

(Second Embodiment)
In the present embodiment, as shown in FIG. 6, an example in which the seal member is changed with respect to the first embodiment will be described.

More specifically, in this embodiment, as shown in the cross-sectional view of FIG. 7, as the sealing member, an annular O-ring 382a disposed in a cylindrical groove formed on the outer periphery of the pressure receiving portion 38a, and the O A resin material 382b disposed on the outer peripheral side of the ring 382a is employed. For this reason, in this embodiment, the flat plate sealing member 381, the shaft side pressing member 381a, the body side pressing member 381b, etc. which were demonstrated in 1st Embodiment are abolished.

The O-ring 382a is a rubber member formed of rubber and is disposed on the outer peripheral side of the pressure receiving portion 38a. The resin material 382b is a cylindrical resin material formed of a resin having a smaller sliding resistance with the upper body 311 than the O-ring 382a. FIG. 7 is a schematic enlarged cross-sectional view of the pressure receiving portion 38a and the like in a state where the shaft 38 is not attached to the upper body 311.

Further, in the present embodiment, since the flat plate sealing member 381 is eliminated, the gap dimension δ is formed smaller than that in the first embodiment, and the pressure receiving portion 38a is slidably supported by the upper body 311. . For this reason, the outer diameter of the pressure receiving portion 38a and the inner diameter of the portion of the upper body 311 that supports the pressure receiving portion 38a are in a dimensional relationship of the clearance fit.

Further, in the upper body 311 of the present embodiment, the first passage 311c that connects the gap between the pressure receiving portion 38a and the upper body 311 and the internal space of the cover member 375, and the internal space of the cover member 375 and the suction passage 13b. The 2nd channel | path 311d which connects with the refrigerant | coolant suction port 31b side is formed.

The first passage 311c and the second passage 311d are suction passages through which the refrigerant flowing out from the inflow space 30a through the gap between the upper body 311 and the pressure receiving portion 38a flows through the suction passage 13b before flowing into the introduction space 37b. It is the 1st passage for a merge made to merge with a refrigerant. Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment.

Therefore, according to the ejector refrigeration cycle 10 of the present embodiment, the COP of the cycle can be improved as in the first embodiment. Furthermore, according to the ejector 13 of the present embodiment, the cross-sectional areas of the nozzle passage 13a and the diffuser passage 13c are appropriately changed according to the load fluctuation of the applied ejector refrigeration cycle 10 as in the first embodiment. can do.

Further, in the ejector 13 of the present embodiment, the seal member is formed of the O-ring 382a and the resin material 382b. According to this, a sealing member can be arrange | positioned easily.

Further, since the resin material 382b is disposed, even if the O-ring 382a is disposed in the pressure receiving portion 38a having a larger outer diameter than other portions of the shaft 38, the sliding resistance when the shaft 38 is displaced is greatly increased. There is no increase. Therefore, when the passage forming member 35 is displaced, it is possible to suppress the responsiveness from being greatly deteriorated and the hysteresis from being greatly increased.

Further, in the ejector 13 of the present embodiment, the first passage 311c and the second passage 311d are formed as the first joining passage. Thereby, even if the high-pressure refrigerant in the inflow space 30a flows out while being reduced in pressure through the gap between the pressure receiving portion 38a and the upper body 311, this refrigerant is merged with the suction refrigerant before flowing into the introduction space 37b. be able to.

Therefore, the refrigerant that has passed through the gap between the pressure receiving portion 38a and the upper body 311 accumulates on one end side of the pressure receiving portion 38a (opposite side of the inflow space 30a) and increases the pressure on one end side of the pressure receiving portion 38a. There is no. As a result, the pressure receiving portion 38a can reliably receive the second load Pw2, and the fluctuation of the first load Pw1 can be canceled with certainty.

Furthermore, the refrigerant that has been depressurized through the gap between the pressure receiving portion 38a and the upper body 311 directly flows into the introduction space 37b and lowers the refrigerant temperature in the introduction space 37b, so-called “cooling”. The occurrence of this problem can be suppressed. Therefore, it is possible to prevent the drive mechanism 37 from generating unnecessary driving force by detecting the temperature of the refrigerant that has been reduced in pressure through the gap between the pressure receiving portion 38a and the upper body 311.

(Third embodiment)
In the present embodiment, as shown in FIG. 8, an example in which the seal member is changed with respect to the first embodiment will be described.

More specifically, in this embodiment, as shown in the cross-sectional view of FIG. 9, the seal member is provided between the end surface on one end side in the axial direction of the pressure receiving portion 38 a (opposite side of the inflow space 30 a) and the upper body 311. An annular seal member 383 arranged in the above is adopted. For this reason, in the present embodiment, as in the second embodiment, the flat plate sealing member 381, the shaft side pressing member 381a, the body side pressing member 381b, and the like are omitted.

The annular seal member 383 is formed in a substantially cylindrical shape with rubber which is an elastic member. As the passage forming member 35 and the shaft 38 are displaced, the annular seal member 383 is sandwiched between the pressure receiving portion 38a and the upper body 311 and deformed.

Therefore, the annular seal member 383 is employed whose axial deformation amount is larger than the lift amount (axial displacement amount) required for the passage forming member 35 to appropriately change the passage sectional area. ing. FIG. 9 is a schematic enlarged cross-sectional view of the pressure receiving portion 38a in a state where the shaft 38 is not attached to the upper body 311.

Further, the upper body 311 of the present embodiment is formed with a first passage 311c and a second passage 311d as first joining passages similar to those of the second embodiment. Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the second embodiment.

Therefore, according to the ejector refrigeration cycle 10 of the present embodiment, the COP of the cycle can be improved as in the first embodiment. Furthermore, according to the ejector 13 of the present embodiment, the cross-sectional areas of the nozzle passage 13a and the diffuser passage 13c are appropriately changed according to the load fluctuation of the applied ejector refrigeration cycle 10 as in the first embodiment. can do.

Further, in the ejector 13 of the present embodiment, the annular seal member 383 is disposed between the end surface on the one end side in the axial direction of the pressure receiving portion 38 a and the upper body 311. According to this, a sealing member can be arrange | positioned very easily.

Furthermore, the annular seal member 383 does not significantly increase the sliding resistance when the shaft 38 is displaced. Accordingly, when the passage forming member 35 is displaced, it is possible to prevent the responsiveness from deteriorating and the hysteresis from increasing.

Further, in the ejector 13 of the present embodiment, the first passage 311c and the second passage 311d are formed as the first joining passage. Therefore, similarly to the second embodiment, the fluctuation of the first load Pw1 can be canceled with certainty, and the drive mechanism 37 can be prevented from generating unnecessary driving force.

(Fourth embodiment)
In this embodiment, as shown in FIG. 10, the O-ring 382a which is a seal member is abolished with respect to the second embodiment. For this reason, the cylindrical groove | channel in which the O-ring 382a is formed in the outer periphery of the pressure receiving part 38a is also abolished. Furthermore, in the present embodiment, an O-ring 384 is disposed in the gap between the outer periphery of the tip portion on one end side of the shaft 38 and the upper body 311. The O-ring 384 is disposed in a cylindrical groove formed in the upper body 311.

The O-ring 384 is not intended to prevent the refrigerant in the inflow space 30a from flowing out through the gap between the upper body 311 and the pressure receiving portion 38a, but between the upper body 311 and the tip of the shaft 38. It is an introduction space sealing member that suppresses the refrigerant flowing out through the gap from directly flowing into the introduction space 37b. Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment.

Therefore, according to the ejector refrigeration cycle 10 of the present embodiment, the COP of the cycle can be improved as in the first embodiment. Furthermore, according to the ejector 13 of the present embodiment, the cross-sectional areas of the nozzle passage 13a and the diffuser passage 13c are appropriately changed according to the load fluctuation of the applied ejector refrigeration cycle 10 as in the first embodiment. can do.

Further, in the ejector 13 of the present embodiment, the first passage 311c and the second passage 311d are formed as the first joining passage. Therefore, similarly to the second embodiment, the fluctuation of the first load Pw1 can be canceled with certainty. Furthermore, since the O-ring 384 serving as the introduction space sealing member is provided, it is possible to prevent the drive mechanism 37 from generating unnecessary drive force.

Further, since the O-ring 384 as the introduction space sealing member has a smaller diameter than the O-ring 382a as the sealing member described in the second embodiment, the sliding resistance when the shaft 38 is displaced is greatly increased. There is no end. Therefore, when the passage forming member 35 is displaced, it is possible to suppress the responsiveness from being greatly deteriorated and the hysteresis from being greatly increased.

(Fifth embodiment)
In the present embodiment, as shown in FIG. 11, an example in which the second merging passage 38b is provided and the first merging passages (the first passage 311c and the second passage 311d) are abolished with respect to the fourth embodiment. Will be explained. In addition, in FIG. 11, illustration of the 1st load Pw1 and the 2nd load Pw2 is abbreviate | omitted for clarification of drawing.

The second joining passage 38b is formed inside the shaft 38. The second merging passage 38b is a passage that guides the refrigerant that has flowed out from the inflow space 30a through the clearance between the upper body 311 and the pressure receiving portion 38a to the downstream side of the diffuser passage 13c. Other configurations and operations of the ejector 13 and the ejector refrigeration cycle 10 are the same as those in the first embodiment.

Therefore, according to the ejector refrigeration cycle 10 of the present embodiment, the COP of the cycle can be improved as in the first embodiment. Furthermore, according to the ejector 13 of the present embodiment, the cross-sectional areas of the nozzle passage 13a and the diffuser passage 13c are appropriately changed according to the load fluctuation of the applied ejector refrigeration cycle 10 as in the first embodiment. can do.

Further, in the ejector 13 of the present embodiment, a second joining passage 38b is formed. Thereby, even if the high-pressure refrigerant in the inflow space 30a flows out while being depressurized through the gap between the pressure receiving portion 38a and the upper body 311, this can be guided to the downstream side of the diffuser passage. Therefore, similarly to the second embodiment, the fluctuation of the first load Pw1 can be canceled with certainty.

Furthermore, since the O-ring 384 is provided, it is possible to suppress the drive mechanism 37 from generating unnecessary drive force, as in the fourth embodiment.

The present disclosure is not limited to the above-described embodiment, and various modifications can be made as follows without departing from the spirit of the present disclosure.

(1) In each of the above-described embodiments, the example in which the pressure receiving portion 38a is formed integrally with the shaft 38 has been described. However, the pressure receiving portion 38a is not limited to this. For example, the cylindrical pressure receiving portion 38a may be formed as a separate member with respect to the shaft 38 and fixed to the shaft 38 by press fitting or the like. Furthermore, the pressure receiving portion 38a does not need to be formed in a cylindrical shape as long as a pressure receiving area for receiving the second load Pw2 is secured. For example, you may form in the truncated cone shape etc. which taper toward the inflow space 30a side.

(2) In the above-described first embodiment, the example in which the synthetic rubber flat seal member 381 is used has been described, but the flat plate seal member is not limited thereto. For example, a flat seal member formed of EPDM containing a base fabric or a resin material (for example, EVOH: ethylene vinyl alcohol copolymer) may be employed.

Here, since the flat plate sealing member is deflected to displace the passage forming member 35 and the shaft 38 in the axial direction, the flat plate sealing member is required to have high durability against repeated stress. Therefore, it is desirable to employ a resin material or the like that has higher durability than synthetic rubber. However, a resin flat seal member is generally less elastic than synthetic rubber.

For this reason, when a resin flat seal member is employed, high-pressure refrigerant leaks from the gap between the one end surface of the pressure receiving portion 38a and the shaft-side pressing member 381a or from the gap between the step portion 311a and the body-side pressing member 381b. There is a risk that.

When such a leak occurs, the flat surface disposed in the planar groove in the gap between the one end side surface of the pressure receiving portion 38a and the shaft side pressing member 381a or the gap between the stepped portion 311a and the body side pressing member 381b. A seal type O-ring or the like may be disposed.

(3) In each of the above-described embodiments, the example in which the central axis CL of the passage forming member 35 of the ejector 13 is arranged in the horizontal direction has been described, but the arrangement of the ejector 13 is not limited to this. For example, as shown in the overall configuration diagram of FIG. 8, the central axis of the passage forming member 35 may be arranged in the vertical direction. In this case, it is desirable that the liquid-phase refrigerant outlet 31c is disposed on the lowermost side of the gas-liquid separation body.

(4) In the above-described second embodiment, the example in which the first joining passage (the first passage 311c and the second passage 311d) is formed has been described. However, the sealing member (the annular O-ring 382a and the resin material 382b) is described. Thus, if the leakage of the high-pressure refrigerant from the gap between the pressure receiving portion 38a and the upper body 311 can be prevented, the first joining passage (the first passage 311c and the second passage 311d) is not an essential configuration.

In the third embodiment described above, an example in which the first merging passage (the first passage 311c and the second passage 311d) is formed has been described. However, the annular seal member 383 allows the pressure receiving portion 38a and the upper body 311 to be separated from each other. If the leakage of the high-pressure refrigerant can be prevented, the first joining passage (the first passage 311c and the second passage 311d) is not an essential configuration.

In the above-described fourth and fifth embodiments, the example in which the O-ring 384 is provided as the introduction space sealing member has been described, but the refrigerant flowing out through the gap between the upper body 311 and the tip of the shaft 38 is Even if it directly flows into the introduction space 37b, the O-ring 384 is not an essential configuration if the problem of “cooling” does not occur.

(5) What is disclosed in each of the above embodiments may be appropriately combined within a practicable range. For example, the second joining passage 38b described in the fifth embodiment may be applied to the ejector 13 described in the second and third embodiments. Of course, when the second joining passage 38b is employed, the first joining passage may be eliminated.

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

For example, in the above-described embodiment, an example in which an engine-driven variable displacement compressor is employed as the compressor 11 has been described. However, as the compressor 11, the operating rate of the compressor is changed by the on / off of an electromagnetic clutch. You may employ | adopt the fixed capacity type compressor which adjusts a refrigerant | coolant discharge capability. Furthermore, you may employ | adopt an electric compressor provided with a fixed displacement type compression mechanism and an electric motor, and act | operating by supplying electric power. In the electric compressor, the refrigerant discharge capacity can be controlled by adjusting the rotation speed of the electric motor.

In the above-described embodiment, an example in which a subcool type heat exchanger is employed as the radiator 12 has been described, but a normal radiator including only the condensing unit 12a may be employed. In addition to a normal radiator, a receiver-integrated condenser that integrates a receiver (receiver) that separates the gas-liquid of the refrigerant radiated by this radiator and stores excess liquid phase refrigerant is adopted. Also good.

Further, the drive mechanism 37 is not limited to the one described in the above embodiment. For example, you may employ | adopt the thermo wax which changes a volume with temperature as a temperature-sensitive medium. Further, a drive device having a shape memory alloy elastic member may be employed.

In the above-described embodiment, the example in which R1234yf is adopted as the refrigerant has been described, but the refrigerant is not limited to this. For example, R134a, R600a, R410A, R404A, R32, R407C, etc. can be employed. 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.

(7) In the above-described embodiment, the example in which the ejector refrigeration cycle 10 according to the present disclosure is applied to a vehicle air conditioner has been described, but the application of the ejector refrigeration cycle 10 is not limited thereto. For example, the present invention may be applied to a stationary air conditioner, a cold / hot storage, a cooling / heating device for a vending machine, and the like.

In the above-described embodiment, the radiator 12 of the ejector refrigeration cycle 10 including the ejector 13 according to the present disclosure is an outdoor heat exchanger that exchanges heat between the refrigerant and the outside air, and the evaporator 14 cools the blown air. Use side heat exchanger. On the other hand, the evaporator 14 may be used as an outdoor heat exchanger that absorbs heat from a heat source such as outside air, and the radiator 12 may be used as a use side heat exchanger that heats a heated fluid such as air or water.

Although the present disclosure has been described with reference to embodiments, it is understood that the present disclosure is not limited to the above-described embodiments and structures. Rather, the present disclosure includes various modifications and modifications within the equivalent scope. In addition, although various elements of the present disclosure have been shown in various combinations and forms, other combinations or forms that include more or fewer elements than those elements, or only one of them. Are within the scope and spirit of the present disclosure.

Claims (10)

An ejector applied to a vapor compression refrigeration cycle apparatus (10),
An inflow space (30a) through which high-pressure refrigerant flows, a decompression space (30b) that decompresses the refrigerant that has flowed out of the inflow space, and a refrigerant flow downstream of the decompression space, which is sucked from the refrigerant suction port (31b). A body (30) having a suction passage (13b) for circulating the refrigerant, and a pressure increasing space (30e) for allowing the jetted refrigerant injected from the decompression space and the suctioned refrigerant sucked through the suction passage to flow in. )When,
At least a part of the passage forming member (35) is disposed in the decompression space and in the boosting space, and has a conical shape whose outer diameter increases as the distance from the decompression space increases. When,
A drive mechanism (37) for displacing the passage forming member;
A rod-shaped member (38) connected to the passage forming member and extending to the inflow space side and slidably supported by the body;
A refrigerant passage formed between an inner peripheral surface of a portion of the body that forms the decompression space and an outer peripheral surface of the passage forming member is a nozzle passage (13a) that functions as a nozzle that decompresses and injects the refrigerant. ) And
A refrigerant passage formed between an inner peripheral surface of a portion of the body that forms the pressurizing space and an outer peripheral surface of the passage forming member is a pressure increasing unit that increases the pressure by mixing the injected refrigerant and the suction refrigerant. A diffuser passage (13c) that functions as
When the load that the passage forming member receives by the refrigerant pressure in the inflow space is the first load (Pw1),
The rod-shaped member includes an ejector having a pressure receiving portion (38a) that receives a second load (Pw2) in a direction that cancels the first load (Pw1) by the refrigerant pressure in the inflow space. The ejector according to claim 1, wherein a pressure receiving area of the pressure receiving portion (38a) is set so that the first load (Pw1) and the second load (Pw2) are equal. The ejector according to claim 1 or 2, further comprising a seal member (381, 382a, 382b, 383) that suppresses the refrigerant in the inflow space from flowing out through a gap between the body and the rod-shaped member. The ejector according to claim 3, wherein the seal member (382a, 382b) is disposed on an outer peripheral side of the pressure receiving portion. The seal member includes a rubber member (382a) disposed on the outer peripheral side of the rod-shaped member, and a resin material (382b) that is disposed on the outer peripheral side of the rubber member and has a lower sliding resistance than the rubber member. The ejector according to claim 4. The pressure receiving portion is formed in a columnar shape,
The ejector according to claim 3, wherein the seal member (383) is disposed between an end face on one end side of the pressure receiving portion and the body. The ejector according to claim 3, wherein the seal member (381) is formed of an annular plate-shaped member, and an inner peripheral side is fixed to the rod-shaped member and an outer peripheral side is fixed to the body. The first body passage (311c, 311d) is formed in the body for joining the refrigerant flowing out from the inflow space through the gap between the body and the rod-shaped member to the suction refrigerant. The ejector according to any one of 6. The drive mechanism forms an enclosed space forming member (372) that forms an enclosed space (37a) in which a temperature-sensitive medium whose pressure changes with temperature changes is enclosed, and an introduction space (37b) into which the suction refrigerant flows. An introduction space forming member (373), and a pressure responsive member (371) that is displaced according to a pressure difference between the pressure of the temperature-sensitive medium and the pressure of the suction refrigerant,
The rod-shaped member is connected to the pressure responsive member,
9. The first merging passage is a passage that joins the refrigerant that has flowed out of the inflow space through a gap between the body and the rod-like member to the suction refrigerant before flowing into the introduction space. The ejector described. The rod-like member has a second merging passage (38b) for guiding the refrigerant flowing out from the inflow space through a gap between the body and the rod-like member to the downstream side of the diffuser passage. The ejector as described in any one of thru | or 6.

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