WO2017212864A1

WO2017212864A1 - Pressure-reducing device

Info

Publication number: WO2017212864A1
Application number: PCT/JP2017/017973
Authority: WO
Inventors: 大介中島; 池上　真; 山田　悦久; 陽一郎河本; 照之堀田
Original assignee: 株式会社デンソー
Priority date: 2016-06-06
Filing date: 2017-05-12
Publication date: 2017-12-14
Also published as: JP2017219230A

Abstract

Provided is a pressure-reducing device comprising a body (30), a valve body (31), a drive section (34), and a support member (32). The body has a rotator-shaped pressure-reducing space (30c) for reducing the pressure of a refrigerant having flowed therein. A part of the valve body is disposed within the pressure-reducing space. The drive section outputs drive force for displacing the valve body. The support member is rotator-shaped and supports the valve body in a slidable manner. A refrigerant passage formed between the outer peripheral surface of the valve body and the inner peripheral surface of the portion of the body, which forms the pressure-reducing space, is a throttle passage (13a) functioning as a throttle for reducing the pressure of a refrigerant. The center axis of the support member is disposed coaxially with the center axis (CL) of the pressure-reducing space. The body has a smallest passage cross-sectional area section (30d) at which the cross-sectional area of the throttle passage is smallest. The support member has a slide region (32a) on which the valve body slides. The smallest passage cross-sectional area section and the slide region overlap each other in the direction perpendicular to the axial direction of the pressure-reducing space.

Description

Decompressor

Cross-reference of related applications

This application is based on Japanese Patent Application No. 2016-112857 filed on June 6, 2016, the contents of which are incorporated herein by reference.

The present disclosure relates to a decompression unit applied to a vapor compression refrigeration cycle apparatus.

Conventionally, Patent Document 1 discloses an ejector as decompression means applied to a vapor compression refrigeration cycle apparatus. In the ejector of this patent document 1, the refrigerant | coolant which flowed out from the evaporator is attracted | sucked through the refrigerant | coolant suction port formed in the body and the suction | inhalation channel | path by the attraction | suction effect | action of the injection refrigerant injected from the nozzle channel | path which pressure-reduces high pressure refrigerant | coolant . Then, the pressure of the mixed refrigerant of the injection refrigerant and the suction refrigerant is increased in the diffuser passage, and flows out to the suction side of the compressor.

More specifically, in the ejector of Patent Document 1, a substantially conical passage forming member (that is, a valve body portion) is disposed in a rotating body-shaped internal space formed inside the body. Thus, a refrigerant passage having an annular cross section is formed between the inner wall surface of the body and the conical side surface of the passage forming member. 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 unit that displaces the passage forming member to change the passage sectional area of the refrigerant passage (that is, 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.

More specifically, the passage forming member is provided with a columnar shaft, and the body is provided with a cylindrical support member that supports the shaft so as to be slidable. The central axis of the support member is arranged coaxially with the central axis of the internal space of the body. Thereby, when the drive unit displaces the passage forming member, the passage is displaced in the axial direction of the internal space to change the passage sectional area of the refrigerant passage.

Japanese Patent Laying-Open No. 2015-137565

However, according to the study of the inventors of the present application, in the configuration in which the shaft of the passage forming member is slidably supported by the support member as in the ejector of Patent Document 1, the outer peripheral surface of the shaft and the inner periphery of the support member are used. A gap is formed between the surfaces. For this reason, the displacement direction of a channel | path formation member and a shaft may incline with respect to the central axis of internal space.

If such an inclination occurs, the cross-sectional shape of the refrigerant passage formed in an annular cross section may become uneven in the circumferential direction. For this reason, even if the drive unit attempts to change the passage cross-sectional area in the throat portion (that is, the minimum passage cross-sectional area portion) of the nozzle passage according to the load variation of the applied refrigeration cycle apparatus, The area may become unstable. As a result, the flow rate of the refrigerant flowing through the nozzle passage may become unstable.

Such a problem is not limited to the ejector, and the valve body portion is arranged in the space forming the throttle passage, and the valve body portion is displaced to change the passage cross-sectional area of the circular throttle passage. The same can occur in the decompression device.

This indication aims at providing the decompression device which can change the passage sectional area of a refrigerant passage with sufficient accuracy according to the driving force outputted from the drive part in view of the above-mentioned point.

The decompression device according to one aspect of the present disclosure is applied to a vapor compression refrigeration cycle apparatus. The decompression device includes a body, a valve body portion, a drive portion, and a support member. The body has a rotator-shaped decompression space that decompresses the refrigerant flowing into the body. At least a part of the valve body is disposed inside the decompression space. The driving unit outputs a driving force that displaces the valve body. The support member has a rotating body shape and supports the valve body portion so as to be slidable. A refrigerant passage formed between the inner peripheral surface of the part of the body forming the decompression space and the outer peripheral surface of the valve body portion is a throttle passage that functions as a throttle for decompressing the refrigerant. The central axis of the support member is arranged coaxially with the central axis of the decompression space. The body has a minimum passage cross-sectional area where the cross-sectional area of the throttle passage is the smallest. The support member has a sliding region in which the valve body portion slides. In the direction perpendicular to the axial direction of the decompression space, the minimum passage cross-sectional area portion and the sliding region overlap.

According to this, when viewed from the direction perpendicular to the axial direction of the decompression space, the minimum passage cross-sectional area overlaps with the sliding region, so that the central axis of the valve body portion is relative to the central axis of the support member. The distance between the rotation center and the minimum passage cross-sectional area when tilting can be shortened.

Here, the rotation center is a point on the central axis of the support member, and can be defined as the axial center point of the sliding region.

Therefore, when the drive unit displaces the valve body, even if the displacement direction of the valve body is inclined with respect to the decompression space and the central axis of the support member, the sectional shape of the throttle passage is not circumferential. The degree of uniformity can be reduced.

As a result, according to one aspect, it is possible to provide a decompression device that can accurately change the passage cross-sectional area of the throttle passage according to the driving force output from the drive unit.

Furthermore, in order to reduce the degree to which the cross-sectional shape of the throttle passage becomes uneven in the circumferential direction and change the passage cross-sectional area of the throttle passage more accurately, the direction perpendicular to the axial direction of the decompression space When viewed from the above, it is desirable that the minimum passage cross-sectional area and the rotation center overlap.

Here, “the minimum passage cross-sectional area and the rotation center overlap” is not limited to the arrangement in which the minimum passage cross-sectional area and the rotation center completely coincide with each other. Even a slight deviation within a range that does not cause instability of the refrigerant flow rate is included in the polymerization.

It is a whole lineblock diagram of the refrigerating cycle device of a 1st embodiment. It is an axial sectional view of the decompression device of a 1st embodiment. It is an axial sectional view of a decompression device of a 2nd embodiment. It is an axial sectional view of the decompression device of other embodiments.

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 and 2. The decompression device 13 of the present embodiment is applied to a vapor compression refrigeration cycle device 10 as shown in FIG. The refrigeration cycle apparatus 10 is applied to a vehicle air conditioner, and fulfills a function of cooling blown air that is blown into a vehicle interior that is an air-conditioning target space. Therefore, the cooling target fluid of the refrigeration cycle apparatus 10 of the present embodiment is blown air.

Further, in the refrigeration cycle apparatus 10 of the present embodiment, R134a is adopted as the refrigerant, and a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant is configured. 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.

Among the components of the refrigeration cycle apparatus 10, the compressor 11 is configured to increase the pressure until the refrigerant is sucked into the high-pressure refrigerant and discharged. 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 30a of the decompression device 13 is connected to the refrigerant outlet side of the supercooling portion 12c of the radiator 12.

The decompression device 13 decompresses the supercooled high-pressure liquid-phase refrigerant that has flowed out of the radiator 12 and flows it downstream. A specific configuration of the decompression device 13 will be described with reference to FIG. In addition, the up and down arrows in FIG. 2 indicate the up and down directions when the decompression device 13 is mounted on the vehicle.

As shown in FIG. 2, the decompression device 13 includes a body 30 formed by combining a plurality of metal components (in this embodiment, aluminum alloy). The body 30 may be made of resin. The body 30 is formed with a refrigerant inlet 30a through which the refrigerant that has flowed out of the radiator 12 flows into the inside, and a refrigerant outlet 30b through which the refrigerant flows out from the inside.

A decompression space 30c is formed in the body 30 to depressurize the refrigerant flowing into the interior from the refrigerant inlet 30a. The decompression space 30c is formed in a rotating body shape in which the tops of two frustoconical spaces arranged on the same axis are coupled to each other via a cylindrical space. Further, a minimum passage cross-sectional area portion 30d that reduces the passage cross-sectional area of the throttle passage 13a, which will be described later, is formed at the central portion in the axial direction of the portion of the body 30 that forms the decompression space 30c.

In addition, 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.

A valve body 31 formed in a truncated cone shape is disposed inside the decompression space 30c. The valve body 31 changes the passage cross-sectional area of the refrigerant passage (that is, the throttle passage) 13a formed inside the decompression device 13 by being displaced in the direction of the central axis CL of the decompression space 30c. The valve body portion 31 is formed of a truncated cone-shaped member made of resin (in this embodiment, made of nylon 6 or nylon 66) having resistance to the refrigerant.

The valve element 31 is formed in a truncated cone shape whose outer diameter decreases toward the downstream side of the refrigerant flow. More specifically, in the decompression device 13 of the present embodiment, the refrigerant inlet 30a is disposed below the refrigerant outlet 30b. Therefore, the valve body 31 is formed in a rotating body shape that tapers from the lower side toward the upper side. Furthermore, the valve body 31 is disposed on the lower side of the decompression space 30c.

For this reason, a refrigerant passage having an annular shape in the axially vertical cross section is formed between the inner peripheral surface of the part forming the decompression space 30c of the body 30 and the outer peripheral surface of the valve body 31. The refrigerant passage is a throttle passage 13a that functions as a throttle for decompressing the refrigerant. In the throttle passage 13a, the passage sectional area decreases from the refrigerant flow upstream side (lower side in the present embodiment) toward the minimum passage sectional area 30d.

Further, a columnar insertion hole 31a is formed on the top side (in the present embodiment, the upper side) of the valve body 31. The central axis of the insertion hole 31 a is arranged coaxially with the central axis of the valve body portion 31. A support member 32 is inserted into the insertion hole 31a. The support member 32 slidably supports the valve body portion 31 and suppresses the displacement direction of the valve body portion 31 from being inclined with respect to the central axis CL direction of the decompression space 30c.

More specifically, the support member 32 is formed of a cylindrical member made of metal (in this embodiment, stainless steel). Therefore, the support member 32 is formed in a rotating body shape. Then, the valve body 31 slides on the support member 32 by inserting one end of the support member 32 (the end on the lower side in the present embodiment) into the insertion hole 31a of the valve body 31. It is supported movably. Therefore, in this embodiment, the area | region which can slide with the internal peripheral surface of the insertion hole 31a among the outer peripheral surfaces of the supporting member 32 becomes the sliding area | region 32a.

Furthermore, as shown in FIG. 2, when viewed from a direction perpendicular to the central axis CL, the minimum passage cross-sectional area 30d is positioned so as to overlap with the sliding region 32a. More specifically, when viewed from a direction perpendicular to the central axis CL, the minimum passage cross-sectional area 30d is the center of rotation when the central axis of the valve body 31 is inclined with respect to the central axis of the support member 32. Polymerized with CP.

Here, the rotation center CP is a point on the central axis of the support member 32 and can be defined as the axial center point of the sliding region 32a. Further, “the minimum passage cross-sectional area 30d is overlapped with the rotation center CP” means that the minimum passage cross-sectional area 30d and the rotation center CP completely coincide when viewed from the direction perpendicular to the central axis CL. It is not limited to arrange | positioning. As described later, it is included in the arrangement so as to be polymerized even if it is slightly deviated as long as the refrigerant flow rate is not destabilized.

Further, the other end of the support member 32 is fixed to the body 30. At this time, the support member 32 is fixed so that the central axis of the support member 32 is arranged coaxially with the central axis CL of the decompression space 30 c of the body 30.

For this reason, ideally, the central axis of the valve body 31 supported by the support member 32 can be arranged coaxially with the central axis CL of the decompression space 30c. However, in practice, there is a gap between the outer peripheral surface of the support member 32 and the inner peripheral surface of the insertion hole 31 a of the valve body portion 31, so that the displacement direction of the valve body portion 31 is the center of the support member 32. It may tilt with respect to the axis.

The operating rod 31b of the valve body 31 is disposed inside the support member 32. The actuating bar 31 b transmits the driving force output from the driving unit 34 to the valve body 31. The actuating rod 31b is formed of a columnar member made of metal (in this embodiment, the same stainless steel as the support member 32).

The operating rod 31b is integrated as a part of the valve body 31 by one end being insert-molded in the valve body 31. The central axis of the operating rod 31b is integrated so as to be arranged coaxially with the central axis of the valve body 31. The other end of the actuating bar 31 b is connected to the drive unit 34.

Furthermore, in this embodiment, the outer diameter of the operating rod 31b is formed smaller than the inner diameter of the support member 32. For this reason, the support member 32 and the operating rod 31b do not slide. Further, an O-ring as a seal member is interposed between the body 30 and the operating rod 31b, so that the refrigerant does not leak from the gap between the body 30 and the operating rod 31b.

The driving unit 34 outputs a driving force that displaces the valve body 31 in the axial direction. In other words, the drive unit 34 changes the passage sectional area of the throttle passage 13a such as the minimum passage sectional area 30d by displacing the valve body 31 in the axial direction. The drive unit 34 of the present embodiment has a stepping motor. The operation of the drive unit 34 is controlled by a control signal (control pulse) output from the control device.

Next, as shown in FIG. 1, the refrigerant inlet side of the evaporator 14 is connected to the refrigerant outlet 30 b of the decompression device 13. The evaporator 14 performs heat exchange between the low-pressure refrigerant decompressed by the decompression device 13 and the blown air blown from the blower fan 14a into the vehicle interior, thereby evaporating the low-pressure refrigerant and exerting an endothermic effect. It is an exchanger.

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. The refrigerant outlet side of the evaporator 14 is connected to the suction port side of the compressor 11.

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, 34, etc. is controlled.

The control device is connected to 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, an evaporator pressure sensor, and a discharge pressure sensor. A detection value is input.

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. An evaporator temperature sensor is an evaporator temperature detection part which detects the temperature of the evaporator 14 exit side refrigerant | coolant. The evaporator pressure sensor is an evaporator pressure detector that detects the pressure of the refrigerant on the outlet side 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 refrigeration cycle apparatus 10 of the present embodiment having the above configuration will be described. 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 refrigeration cycle apparatus 10 increases.

The high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the radiator 12, exchanges heat with the outside air blown from the cooling fan 12d, radiates heat, and becomes a supercooled liquid phase refrigerant. The supercooled liquid phase refrigerant flowing out of the radiator 12 is decompressed by the decompression device 13 and becomes a low-pressure refrigerant.

At this time, the controller reduces the pressure reducing device so that the superheat degree of the refrigerant on the outlet side of the evaporator 14 calculated from the detected value of the evaporator temperature sensor and the detected value of the evaporator pressure sensor approaches the predetermined reference superheat degree KSH. The operation of the 13 drive units 34 is controlled. That is, the control device adjusts the passage cross-sectional area of the minimum passage cross-sectional area 30d of the throttle passage 13a so that the superheat degree of the evaporator 14 outlet-side refrigerant approaches the reference superheat degree KSH.

The low-pressure refrigerant decompressed by the decompression device 13 flows into the evaporator 14, absorbs heat from the blown air blown by the blower fan 14a, and evaporates. Thereby, blowing air is cooled. The refrigerant flowing out of the evaporator 14 is sucked into the compressor 11 and compressed again. The refrigeration cycle apparatus 10 according to the present embodiment operates as described above and can cool the blown air blown into the vehicle interior.

By the way, in the decompression device 13 of the present embodiment, since there is a gap between the outer peripheral surface of the support member 32 and the inner peripheral surface of the insertion hole 31a of the valve body portion 31, as described above, The displacement direction may be inclined with respect to the central axis of the support member 32. When such an inclination occurs, the cross-sectional shape of the throttle passage 13a formed in an annular cross-section becomes uneven in the circumferential direction.

For this reason, even if the drive unit 34 attempts to change the passage sectional area in the minimum passage sectional area 30d of the throttle passage 13a in accordance with the load fluctuation of the refrigeration cycle apparatus 10, the passage sectional area in the minimum passage sectional area 30d is reduced. It becomes unstable. As a result, the flow rate of the refrigerant flowing through the throttle passage 13a may become unstable.

On the other hand, in the decompression device 13 of the present embodiment, when viewed from the direction perpendicular to the central axis CL of the decompression space 30c, the minimum passage cross-sectional area 30d overlaps with the sliding region 32a. For this reason, the distance between the rotation center CP and the minimum passage cross-sectional area 30d when the central axis of the valve body 31 is inclined with respect to the central axis of the support member 32 can be shortened.

Therefore, when the drive part 34 displaces the valve body part 31, even if the displacement direction of the valve body part 31 is inclined with respect to the central axis of the decompression space 30c and the support member 32, the cross section of the throttle passage 13a. The degree to which the shape becomes nonuniform in the circumferential direction can be reduced.

As a result, according to the decompression device 13 of the present embodiment, the passage sectional area in the minimum passage sectional area 30d of the throttle passage 13a can be accurately changed according to the driving force output from the driving unit 34.

Here, the passage cross-sectional area of the minimum passage cross-sectional area portion 30d of the throttle passage 13a is the minimum passage cross-sectional area that determines the flow rate of the refrigerant flowing through the throttle passage 13a. Therefore, the ability to reduce the degree to which the cross-sectional shape of the minimum passage cross-sectional area 30d of the throttle passage 13a becomes uneven in the circumferential direction is extremely effective for stabilizing the flow rate of the refrigerant flowing through the decompression device 13.

Furthermore, in the decompression device 13 of the present embodiment, since the minimum passage cross-sectional area 30d and the rotation center CP are arranged so as to overlap when viewed from the direction perpendicular to the central axis CL, the sectional shape of the throttle passage 13a. The degree of non-uniformity in the circumferential direction can be effectively reduced, and the passage cross-sectional area in the minimum passage cross-sectional area 30d of the throttle passage 13a can be changed with higher accuracy.

(Second Embodiment)
This embodiment demonstrates the example which changed the valve body part 31 and the support member 32 with respect to 1st Embodiment. More specifically, in this embodiment, as shown in FIG. 3, an insertion hole 31 a is formed on the bottom surface of the valve body portion 31 (the lower surface in the present embodiment). The valve body 31 is slidably supported by the support member 32 by inserting one end of the support member 32 (the upper end in the present embodiment) into the insertion hole 31a. ing.

That is, in the present embodiment, the operating rod 31b is formed in a shape extending from the valve body portion 31 toward one axial side of the central axis CL (in the present embodiment, the upper side). Further, the support member 32 is formed in a shape extending from the valve body portion 31 toward the other axial side of the central axis CL (in the present embodiment, the lower side).

The other end of the support member 32 is fixed to the bottom surface of the body 30. At this time, the support member 32 is fixed so that the central axis of the support member 32 is arranged coaxially with the central axis CL of the decompression space 30 c of the body 30.

Further, a coil spring 35, which is an elastic member that applies a load in a direction to reduce the passage cross-sectional area of the minimum passage cross-sectional area 30d to the valve body 31, is accommodated in the support member 32. The coil spring 35 also functions as a vibration suppressing member that attenuates the vibration of the valve body 31 caused by pressure pulsation when the refrigerant is depressurized or vibration transmitted from the outside.

Furthermore, as shown in FIG. 3, when viewed from a direction perpendicular to the central axis CL, the minimum passage cross-sectional area 30d is positioned within a range where it overlaps with the sliding region 32a. More specifically, when viewed from a direction perpendicular to the central axis CL, the minimum passage cross-sectional area 30d is the center of rotation when the central axis of the valve body 31 is inclined with respect to the central axis of the support member 32. Arranged to polymerize with CP. Other configurations and operations are the same as those in the first embodiment.

Therefore, also in the decompression device of the present embodiment, similarly to the first embodiment, the passage cross-sectional area in the minimum passage cross-sectional area 30d of the throttle passage 13a is accurately changed according to the driving force output from the driving unit 34. Can be made. In FIG. 3, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.

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. In addition, the means disclosed in each embodiment may be appropriately combined within a practicable range.

In the above-described embodiment, the example in which the refrigerant inlet 30a is disposed below the refrigerant outlet 30b has been described. However, the refrigerant inlet 30a may be disposed above the refrigerant outlet 30b. That is, as shown in FIG. 4, the refrigerant may flow in the opposite direction to the first and second embodiments.

In the above-described embodiment, the decompression space 30c is formed in a rotating body shape in which the top sides of the two truncated cone-shaped spaces arranged coaxially are coupled to each other via a cylindrical space. Although described, the shape of the decompression space 30c is not limited to this. If the minimum passage cross-sectional area 30d can be formed, for example, as shown in FIG. 4, it is a rotating body shape in which the top sides of two frustoconical spaces arranged coaxially are directly coupled to each other. Also good.

Moreover, although the above-mentioned embodiment demonstrated the example which employ | adopted what was formed in the truncated cone shape as the valve body part 31, the valve body part 31 is not limited to this. For example, as shown in FIG. 4, it may be formed in a spherical shape, or may be formed in a hemispherical shape, a cylindrical shape, or the like. Furthermore, the valve body portion 31 may be formed of metal.

In the above-described embodiment, the example in which the support member 32 is formed in a cylindrical shape has been described. However, the support member 32 is not limited to a cylindrical shape as long as it is formed in a rotating body shape. For example, the support member 32 may be formed in a columnar shape.

Moreover, although the above-mentioned embodiment demonstrated the example which slid the inner peripheral surface of the insertion hole 31a of the valve body part 31 and the outer peripheral surface of the support member 32, the valve body part 31, the support member 32, and The sliding portion is not limited to this. For example, as shown in FIG. 4, the outer peripheral surface of the operating rod 31 b that is a part of the valve body 31 and the support member 32 without sliding the inner peripheral surface of the insertion hole 31 a and the outer peripheral surface of the support member 32. You may make it slide with an inner peripheral surface.

In the above-described embodiment, an example in which an electric drive mechanism configured by including a stepping motor as the drive unit 34 has been described, but the drive unit is not limited thereto. For example, a temperature sensing unit that detects the degree of superheat of the evaporator 14 outlet-side refrigerant based on the temperature and pressure of the evaporator 14 outlet-side refrigerant so that the superheat degree of the evaporator 14 outlet-side refrigerant approaches the reference superheat degree. Alternatively, a mechanical drive mechanism for adjusting the valve opening degree may be used.

Specifically, such a mechanical drive mechanism includes an enclosed space forming member that forms an enclosed space in which a temperature sensitive medium that changes in pressure according to the temperature of the refrigerant on the outlet side of the evaporator 14 is enclosed, and a temperature sensitive medium. And a pressure responsive member that displaces according to the pressure difference between the pressure of the evaporator 14 outlet side refrigerant, and a drive mechanism that transmits the displacement of the pressure responsive member to the valve body 31 can be employed.

Each component apparatus which comprises the refrigerating-cycle apparatus 10 is not limited to what was disclosed by the above-mentioned 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.

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

In the above-described embodiment, an example in which the refrigeration cycle apparatus 10 according to the present disclosure is applied to a vehicle air conditioner has been described, but application of the refrigeration cycle apparatus 10 is not limited to this. 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 refrigeration cycle apparatus 10 including the decompression device 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 based on the embodiments, it is understood that the present disclosure is not limited to the embodiments and structures. The present disclosure includes various modifications and modifications within the equivalent range. In addition, although various combinations and forms are shown in the present disclosure, other combinations and forms including only one element, more or less than them are also included in the scope and concept of the present disclosure. Is.

Claims

A decompression device applied to a vapor compression refrigeration cycle device (10),
A body (30) in which a pressure reducing space (30c) having a rotating body for reducing the pressure of the refrigerant flowing into the interior is formed;
A valve body portion (31) at least partially disposed inside the decompression space;
A drive unit (34) for outputting a drive force for displacing the valve body unit;
A rotating body-shaped support member (32) that slidably supports the valve body portion,
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 valve body portion is a throttle passage (13a) that functions as a throttle for decompressing the refrigerant. ,
The central axis of the support member is arranged coaxially with the central axis (CL) of the decompression space,
The body has a minimum passage cross-sectional area (30d) where the cross-sectional area of the throttle passage is reduced most,
The support member has a sliding region (32a) in which the valve body slides,
A decompression device in which the minimum passage cross-sectional area portion and the sliding region overlap in a direction perpendicular to the axial direction of the decompression space.
A point on the central axis of the support member, the axial center point of the sliding region is defined as the rotation center (CP);
The decompression device according to claim 1, wherein the decompression device is arranged so that the minimum passage cross-sectional area and the rotation center overlap in a direction perpendicular to the axial direction of the decompression space.
The valve body portion is formed with an insertion hole (31a) into which the support member is inserted,
3. The decompression device according to claim 1, wherein in the sliding region, the outer peripheral surface of the support member and the inner peripheral surface of the insertion hole are arranged to slide.
The valve body portion has a columnar operating rod (31b) connected to the drive portion,
The decompression device according to claim 1 or 2, wherein in the sliding region, the inner peripheral surface of the support member and the outer peripheral surface of the operating rod are arranged to slide.
The valve body portion has a columnar operating rod (31b) connected to the drive portion,
The actuating rod extends from the valve body portion toward one axial side of the central axis,
The decompression device according to claim 1, wherein the support member is formed in a shape extending from the valve body portion to the other axial side of the central axis.