WO2014061056A1 - Dispositif d'étranglement, et dispositif de cycle frigorifique - Google Patents

Dispositif d'étranglement, et dispositif de cycle frigorifique Download PDF

Info

Publication number
WO2014061056A1
WO2014061056A1 PCT/JP2012/006613 JP2012006613W WO2014061056A1 WO 2014061056 A1 WO2014061056 A1 WO 2014061056A1 JP 2012006613 W JP2012006613 W JP 2012006613W WO 2014061056 A1 WO2014061056 A1 WO 2014061056A1
Authority
WO
WIPO (PCT)
Prior art keywords
main body
valve
flow path
refrigerant
flow
Prior art date
Application number
PCT/JP2012/006613
Other languages
English (en)
Japanese (ja)
Inventor
裕輔 島津
幸志 東
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2012/006613 priority Critical patent/WO2014061056A1/fr
Priority to CN201390000811.0U priority patent/CN204628600U/zh
Priority to JP2014542001A priority patent/JP5881845B2/ja
Priority to PCT/JP2013/074860 priority patent/WO2014061385A1/fr
Priority to CN201320634382.4U priority patent/CN203550354U/zh
Publication of WO2014061056A1 publication Critical patent/WO2014061056A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/42—Valve seats
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/04—Means in valves for absorbing fluid energy for decreasing pressure or noise level, the throttle being incorporated in the closure member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F25B41/35—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by rotary motors, e.g. by stepping motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present invention relates to a throttle device that adjusts the flow rate of a fluid, and a refrigeration cycle device including the throttle device.
  • fluid noise (refrigerant sound) is generated when the refrigerant passes through a valve chamber equipped with a valve element.
  • fluid noise refrigerant sound
  • the pressure fluctuations occur because the gas phase and the liquid phase alternately and discontinuously pass through the throttle formed by the valve body and the valve chamber.
  • a refrigerant noise may be generated.
  • the pressure is reduced on the downstream side of the throttle portion, the flow is a two-phase flow, and refrigerant noise may be generated due to bubble disturbance or collision.
  • various devices and proposals have been conventionally made.
  • a throttling device there is one that reduces a refrigerant sound by subdividing bubbles in a two-phase refrigerant by providing a thin plate member having a plurality of small holes in the refrigerant flow path (for example, Patent Document 1). reference).
  • Patent Document 1 there is a configuration in which a flow path shape is provided in the valve chamber to form a plurality of flow paths, thereby reducing the kinetic energy of the refrigerant jet, reducing the pressure fluctuation, and reducing the refrigerant sound (for example, Patent Document 2). reference).
  • a partition member is mounted in the valve chamber, and a communication path that connects the fluid inlet side space and the fluid outlet side space is provided in the partition member (for example, see Patent Document 3).
  • JP 2007-107623 A Japanese Patent Laying-Open No. 2005-351605 (paragraphs [0047] and [0053]) JP 2006-207852 A (paragraph [0036])
  • Patent Documents 1 to 3 capture the flow of fluid in a one-dimensional manner and take measures to reduce fluid noise. By collecting the flow after passing through a plurality of paths, the refrigerant flow is reduced. Although it tries to homogenize, it does not mention the influence of the flow direction of a plurality of paths, and the effect of reducing fluid sound is small. Focusing on the process from a plurality of routes to a single flow, a measure to further suppress the flow noise is desired.
  • the present invention has been made to solve the above-described problems, and provides a throttling device capable of suppressing the fluid sound of the fluid flowing through the throttling device, and a refrigeration cycle device including the throttling device. .
  • a throttling device includes a main body to which a first flow path and a second flow path are connected, a valve chamber formed inside the main body and communicating with the first flow path, and formed in the valve chamber.
  • a valve seat having an opening communicating with the second flow path; and a valve body that is provided so as to be movable forward and backward toward the opening of the valve seat and adjusts an opening degree of the opening.
  • a plurality of main body flow paths communicating with the passage and the opening of the valve seat are formed, and the flow direction of the plurality of main body flow paths is formed at an angle with the axial direction of the valve body.
  • a plurality of main body flow paths communicating the second flow path and the opening of the valve seat are formed, and the flow direction of the plurality of main body flow paths is formed at an angle with the axial direction of the valve body. Yes.
  • fluid energy can be reduced by effectively dispersing the fluid flow, and fluid sound can be reduced.
  • FIG. 3 is a cross-sectional view taken along line AA in FIG. 2.
  • FIG. 3 is a cross-sectional view taken along the line BB in FIG. 2. It is a forward direction flow velocity distribution of the throttle apparatus in Embodiment 1 of this invention. It is a reverse direction flow velocity distribution of the diaphragm
  • a case where the present invention is applied to a throttle device that adjusts the flow rate of refrigerant in a refrigeration cycle device will be described as an example.
  • the throttling device of the present invention is not limited to adjusting the flow rate of the refrigerant, and can be applied to any fluid.
  • FIG. 1 is a diagram showing a configuration of a diaphragm device according to Embodiment 1 of the present invention.
  • FIG. 2 is a cross-sectional view of a main part of the diaphragm device according to Embodiment 1 of the present invention.
  • 3 is a cross-sectional view taken along the line AA in FIG. 4 is a cross-sectional view taken along line BB in FIG.
  • FIG. 2 shows a case where the opening of the expansion device is fully closed.
  • the expansion device 100 includes a main body 1 to which the first flow path 2 and the second flow path 3 are connected, a valve chamber 14 that is formed inside the main body 1 and communicates with the first flow path 2, A valve seat 10 having an orifice 11 formed in the valve chamber 14 and communicating with the second flow path 3; and a valve body 4 which is provided so as to be movable forward and backward toward the orifice 11 of the valve seat 10 and adjusts the opening degree of the orifice 11. It has.
  • the orifice 11 corresponds to the “opening of the valve seat” in the present invention.
  • the main body 1 has, for example, a cylindrical shape.
  • the 1st flow path 2 and the 2nd flow path 3 are comprised by refrigerant
  • coolant piping is inserted in the opening part of the main body 1, and is fixed by joining means, such as brazing.
  • the first flow path 2 is provided in the radial direction of the main body 1.
  • the second flow path 3 is provided on the axis of the main body 1. That is, the first flow path 2 and the second flow path 3 are provided in directions orthogonal to each other.
  • a stepping motor 20 constituted by a rotor connected to the valve body 4 via a moving mechanism (not shown) and a stator is provided on the upper part of the valve body 4.
  • the rotation of the stepping motor 20 is converted into a translation distance by the moving mechanism, and the valve body 4 moves in the axial direction (vertical direction) to control the opening degree of the valve seat 10.
  • the valve body 4 includes a valve body body portion 5 penetrating the valve chamber 14, a valve body tip portion 7 having a smaller diameter than the opening of the orifice 11 of the valve seat 10, and the valve body body portion 5 and the valve body tip portion. 7 is connected to the needle portion 6. Further, on a substantially central axis of the valve body body portion 5, for example, a cylindrical valve body tip portion 7 is formed. A valve body distal end portion 7 of the valve body 4 is fitted to the main body bearing portion 9 so as to be rotatable and movable in the axial direction.
  • tip part 7 is not limited to a cylinder.
  • the main body 1 is formed with a main body bearing portion 9 that supports the valve body 4.
  • the main body bearing portion 9 is formed by a main body flow path 13 through which the refrigerant (fluid) flows through the second flow path 3 and the orifice 11 and a valve body support hole 12 into which the valve body front end portion 7 is fitted.
  • the valve body support hole 12 is formed by an insertion hole having an inner diameter slightly larger than the outer diameter of the valve body tip 7 of the valve body 4, and the valve body tip 7 of the valve body 4 is slidable. By being inserted into the valve body, the valve body 4 is supported in sliding contact with the valve body tip portion 7.
  • a plurality of main body flow paths 13 are formed around the valve body distal end portion 7.
  • the plurality of main body flow paths 13 are each formed in a circular shape, and are arranged at substantially equal intervals on a circumference concentric with the orifice 11, for example, as shown in FIGS. 3 and 4.
  • the main body flow path 13 is formed such that the refrigerant flow direction forms an angle with the axial direction of the valve body 4, that is, the axial direction of the second flow path 3.
  • the main body flow path 13 forms a flow path that is inclined from the orifice 11 toward the outer peripheral direction of the second flow path 3.
  • the plurality of main body channels 13 are formed such that the interval between the orifices 11 is narrower than the interval between the second channels 3.
  • the central axes of the plurality of main body flow paths 13 are formed so as to spread outward from the orifice 11 side toward the second flow path 3 side. Further, the main body bearing portion 9 is disposed at a distance from the orifice 11, and the plurality of main body flow paths 13 communicate with each other between the orifice 11 and the main body bearing portion 9.
  • the refrigerant traveling from the second flow path 3 to the first flow path 2 is divided into a plurality of main body flow paths 13, and then merges again between the main body bearing portion 9 and the orifice 11 to reach the orifice 11. .
  • the valve body 4 is further moved upward and the flow passage area between the needle portion 6 of the valve body 4 and the valve seat 10 is maximized (full opening degree), the flow rate is restricted by the orifice 11. (Second stage aperture).
  • the valve body 4 slides downward. And the needle part 6 and the valve seat 10 of the valve body 4 contact
  • the gas-phase refrigerant may be mixed in the liquid-phase refrigerant as foam.
  • this gas-liquid mixed refrigerant passes through the expansion device 100, it causes noise. It has been found that the main cause of noise is the presence of gas-phase refrigerant foam, and particularly the presence of large foam is a problem.
  • FIG. 13 is a cross-sectional view of a main part of a conventional diaphragm device.
  • FIG. 13 shows a case where the opening degree of the expansion device is fully closed.
  • the valve body tip portion 7, the body bearing portion 9, the valve body support hole 12, and the plurality of body flow paths 13. Is not provided.
  • the direction in which the refrigerant flows from the first flow path 2 to the second flow path 3 is the forward flow
  • the direction in which the refrigerant flows from the second flow path 3 to the first flow path 2 is the reverse direction.
  • Let it flow. 14 and 15 show the results of analysis of the average velocity field when a predetermined opening degree and a predetermined differential pressure are applied to the forward flow and the reverse flow in the conventional throttle device.
  • FIG. 14 is a forward flow velocity distribution of a conventional throttle device.
  • the refrigerant speed is low in the first flow path 2 and the valve chamber 14.
  • the speed of the refrigerant increases in a narrow flow path between the needle portion 6 and the valve seat 10 and flows so as to narrow in a conical shape along the needle portion 6.
  • it enters the second flow path 3 but flows so as to narrow in a conical shape due to inertia.
  • kinetic energy is concentrated and the refrigerant speed is increased.
  • the influence of the pressure fluctuation on the other refrigerant flows is very large because each flow is concentrated.
  • the coolant speed is very high in the second flow path 3 around the orifice 11.
  • FIG. 15 is a reverse flow velocity distribution of the conventional throttle device.
  • the refrigerant speed is low in most regions.
  • the refrigerant speed is small in the second flow path 3 and the orifice.
  • the speed of the refrigerant increases in a narrow flow path between the needle portion 6 and the valve seat 10, and flows so as to spread conically along the needle portion 6. When leaving this narrow area, it enters into the valve chamber 14 but flows so as to spread conically due to inertia. As a result, kinetic energy diffuses and the refrigerant speed is low. Further, even if there is a pressure fluctuation at a certain position of the valve chamber 14, the influence of the pressure fluctuation on the other refrigerant flows is small because each flow is away.
  • the reverse flow shown in FIG. 15 is less in the region where the refrigerant speed is higher and the refrigerant sound is lower than the forward flow shown in FIG. Even in the actual observation result, the refrigerant noise is smaller in the reverse flow than in the normal flow. That is, in order to suppress the refrigerant noise, the flow of the fluid inside the throttling device may be a flow that spreads in the traveling direction, as in the flow of fluid in FIG.
  • FIG. 5 and FIG. 6 show the analysis results of the average velocity field when a predetermined opening degree and a predetermined differential pressure are applied to the forward flow and the reverse flow in the expansion device 100 according to the first embodiment. .
  • FIG. 5 is a forward flow velocity distribution of the throttle device according to Embodiment 1 of the present invention.
  • the refrigerant speed is low in most regions.
  • the speed of the refrigerant is low.
  • the speed of the refrigerant increases in a narrow flow path between the needle portion 6 and the valve seat 10 and flows so as to narrow in a conical shape along the needle portion 6.
  • the valve body tip portion 7 is present, the flow is not concentrated in the center.
  • the refrigerant flows in a direction in which the flow is divided and dispersed by passing through the plurality of main body flow paths 13.
  • FIG. 6 is a reverse flow velocity distribution of the throttle device according to Embodiment 1 of the present invention.
  • the refrigerant speed is low in most regions.
  • the speed of the refrigerant increases in a narrow flow path between the needle portion 6 and the valve seat 10, and flows so as to spread conically along the needle portion 6. When leaving this narrow area, it enters into the valve chamber 14 but flows so as to spread conically due to inertia. As a result, kinetic energy diffuses and the refrigerant speed is low.
  • the reverse flow of the expansion device 100 according to the first embodiment shown in FIG. 6 has an average velocity field substantially similar to the reverse flow of the conventional expansion device shown in FIG.
  • a plurality of main body flow paths 13 that connect the orifice 11 and the second flow path 3 are formed between the orifice 11 and the second flow path 3. ing. For this reason, it is possible to reduce the fluid energy by effectively dispersing the refrigerant flow, to reduce the region where the refrigerant speed becomes high, to suppress an increase in pressure fluctuation, and to reduce the refrigerant sound (fluid sound). Can do.
  • the expansion device 100 according to the first embodiment is formed such that the total flow area of the plurality of main body flow paths 13 is larger than the flow area of the orifice 11. Therefore, even if the opening degree of the orifice 11 changes from fully closed to fully open, the plurality of main body flow paths 13 do not become a main factor for determining the flow rate. Therefore, for example, the expansion device 100 according to the first embodiment in which the plurality of main body flow paths 13 are provided and the conventional expansion device in which the plurality of main body flow paths 13 are not provided coexist in the same refrigeration cycle apparatus. However, since the flow characteristics can be made almost common, the manufacturing cost can be reduced.
  • FIG. 7 is a schematic diagram for explaining the effects of the diaphragm device according to the first embodiment of the present invention in a plurality of paths.
  • FIG. 7A shows a conventional throttling device, and shows a case where the channel lengths La of the plurality of body channels 13 are shorter than the closest distance Da of the plurality of body channels 13 (Da> La).
  • FIG. 7B shows the expansion device 100 according to the first embodiment, and the flow length Lb of the plurality of main body flow paths 13 is longer than the closest distance Db of the plurality of main body flow paths 13 (Db ⁇ Lb).
  • FIG. 8 is a cross-sectional view of a main part of the diaphragm device according to Embodiment 1 of the present invention.
  • the expansion device 100 according to the first embodiment is formed such that the distance W from the end of the plurality of main body flow paths 13 on the orifice 11 side to the valve seat 10 is smaller than the opening width R of the orifice 11. Has been.
  • the refrigerant that has flowed so as to narrow in a conical shape along the needle portion 6 of the valve body 4 is concentrated in the center, or turbulence occurs, resulting in refrigerant velocity distribution fluctuations and pressure fluctuations, resulting in refrigerant noise.
  • the distance W is made smaller than the opening width R, it is possible to suppress aggregation and turbulence of the refrigerant flow between the end of the plurality of main body flow paths 13 on the orifice 11 side and the valve seat 10.
  • refrigerant noise can be further suppressed.
  • FIG. 9 is a diagram showing another configuration example of the diaphragm device according to Embodiment 1 of the present invention. As shown in FIG. 9, the valve body distal end portion 7, the main body bearing portion 9, and the valve body support hole 12 may be omitted, and a plurality of main body flow paths 13 may be formed around the central portion 17. Even in such a configuration, the above-described effects can be achieved.
  • a plurality of main body flow paths 13 are formed in the main body 1 .
  • the present invention is not limited to this and may be formed separately from the main body 1.
  • a plurality of main body flow paths 13 may be formed in a cylindrical member, and the cylindrical members may be arranged at a distance W on the second flow path 3 side of the orifice 11.
  • FIG. FIG. 10 is a diagram for explaining the occurrence of stagnation and vortices in the diaphragm device. As shown in FIG. 10, when the refrigerant that has passed through the plurality of main body flow paths 13 flows into the second flow path 3, stagnation and vortex of the refrigerant flow may occur. Such stagnation and vortex of the refrigerant flow may cause refrigerant noise.
  • FIG. 11 is a cross-sectional view of a main part of the diaphragm device according to Embodiment 2 of the present invention.
  • the expansion device 100 according to the second embodiment of the present invention has a main body bearing portion on the second flow path 3 side of the main body bearing portion 9 (center portion).
  • a stationary member 15 extending from 9 (center portion) to the second flow path 3 is provided. Accordingly, the refrigerant that has passed through the plurality of main body flow paths 13 flows along the flow path between the stationary member 15 and the inner wall of the second flow path 3, and can suppress the stagnation of the refrigerant flow and the generation of vortices. Therefore, the refrigerant noise can be suppressed.
  • the shape of the stationary member 15 is a conical shape whose diameter increases from the end of the main body bearing portion 9 to the second flow path 3 side along the flow direction of the plurality of main body flow paths 13. And has a conical shape with a reduced diameter after a predetermined distance from the inner wall of the second flow path 3 so that the refrigerant flowing through the inner wall side of the second flow path 3 diffuses.
  • FIG. 12 is a diagram illustrating a configuration of the refrigeration cycle apparatus according to Embodiment 3 of the present invention.
  • the refrigeration cycle apparatus includes a compressor 110, a condenser 120, an expansion device 100, and an evaporator 130, which are sequentially connected by refrigerant piping to form a refrigerant circuit.
  • Compressor 110 compresses the refrigerant and flows it into condenser 120.
  • the condenser 120 condenses the refrigerant compressed by the compressor 110.
  • the expansion device 100 is connected to the condenser 120 through a refrigerant pipe constituting the first flow path 2, and expands the refrigerant condensed by the condenser 120. Further, the expansion device 100 is connected to the evaporator 130 by a refrigerant pipe constituting the second flow path 3. The evaporator 130 evaporates the refrigerant expanded by the expansion device 100.
  • the low-pressure gas refrigerant when the compressor 110 is started, the low-pressure gas refrigerant is sucked into the compressor 110 and compressed to become a high-pressure gas refrigerant.
  • the high-pressure gas refrigerant is condensed by the condenser 120 to become a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant is decompressed by the expansion device 100 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant, and is evaporated by the evaporator 130 to become a low-pressure gas refrigerant. This low-pressure gas refrigerant is sucked into the compressor 110 again.
  • This refrigeration cycle apparatus can be used, for example, in an air conditioner or the like, and performs heating using heat generated in the condenser 120. In addition, cooling is performed using the heat absorption of the evaporator 130.
  • the evaporator 130 may be connected to the refrigerant pipe constituting the first flow path 2 of the expansion device 100, and the condenser 120 may be connected to the refrigerant pipe constituting the second flow path 3. Further, a cooling / heating operation may be switched by providing a four-way valve to change the circulation direction of the refrigerant.
  • the refrigeration cycle apparatus can suppress refrigerant noise.
  • the expansion device 100 is arranged on the load side (inside the room), it is possible to make it difficult for people in the room to hear the refrigerant sound, and to improve comfort.
  • Main body 1. Main body, 2. First flow path, 3. Second flow path, 4. Valve body, 5. Valve body body part, 6. Needle part, 7. Valve body tip, 9. Main body bearing part, 10. Valve seat, 11. Orifice, 12. Valve body. Support hole, 13 body flow path, 14 valve chamber, 15 stationary member, 17 central part, 20 stepping motor, 100 throttle device, 110 compressor, 120 condenser, 130 evaporator, 200 refrigeration cycle apparatus.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Details Of Valves (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Lift Valve (AREA)

Abstract

Le dispositif d'étranglement de l'invention est équipé : d'un corps principal (1) dans lequel un premier et un second trajet d'écoulement (2, 3) sont connectés ; d'une chambre de soupape (14) qui est formée dans la partie interne du corps principal (1), et qui communique avec le premier trajet d'écoulement (2) ; d'un siège de soupape (10) qui est formé dans la chambre de soupape (14), et qui possède une ouverture communiquant avec le second trajet d'écoulement (3) ; et d'un corps de soupape (4) qui est agencé de manière à avancer et à se retirer librement par rapport à l'ouverture du siège de soupape (10), régulant ainsi le degré d'ouverture de cette ouverture. Le corps principal (1) présente une pluralité de trajets d'écoulement de corps principal (13) formée de manière à faire communiquer le second trajet d'écoulement (3) et l'ouverture du siège de soupape (10), et est formé de sorte que la direction d'écoulement de cette pluralité de trajets d'écoulement de corps principal (13), constitue un angle vis-à-vis de la direction axiale du corps de soupape (4).
PCT/JP2012/006613 2012-10-16 2012-10-16 Dispositif d'étranglement, et dispositif de cycle frigorifique WO2014061056A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
PCT/JP2012/006613 WO2014061056A1 (fr) 2012-10-16 2012-10-16 Dispositif d'étranglement, et dispositif de cycle frigorifique
CN201390000811.0U CN204628600U (zh) 2012-10-16 2013-09-13 节流装置以及制冷循环装置
JP2014542001A JP5881845B2 (ja) 2012-10-16 2013-09-13 絞り装置、および冷凍サイクル装置
PCT/JP2013/074860 WO2014061385A1 (fr) 2012-10-16 2013-09-13 Dispositif d'étranglement, et dispositif de cycle frigorifique
CN201320634382.4U CN203550354U (zh) 2012-10-16 2013-10-15 节流装置及制冷循环装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2012/006613 WO2014061056A1 (fr) 2012-10-16 2012-10-16 Dispositif d'étranglement, et dispositif de cycle frigorifique

Publications (1)

Publication Number Publication Date
WO2014061056A1 true WO2014061056A1 (fr) 2014-04-24

Family

ID=50487654

Family Applications (2)

Application Number Title Priority Date Filing Date
PCT/JP2012/006613 WO2014061056A1 (fr) 2012-10-16 2012-10-16 Dispositif d'étranglement, et dispositif de cycle frigorifique
PCT/JP2013/074860 WO2014061385A1 (fr) 2012-10-16 2013-09-13 Dispositif d'étranglement, et dispositif de cycle frigorifique

Family Applications After (1)

Application Number Title Priority Date Filing Date
PCT/JP2013/074860 WO2014061385A1 (fr) 2012-10-16 2013-09-13 Dispositif d'étranglement, et dispositif de cycle frigorifique

Country Status (2)

Country Link
CN (1) CN204628600U (fr)
WO (2) WO2014061056A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6910159B2 (ja) * 2017-02-24 2021-07-28 三菱電機株式会社 調理器
CN114251462A (zh) * 2020-09-24 2022-03-29 浙江盾安人工环境股份有限公司 电子膨胀阀

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0519766U (ja) * 1991-08-30 1993-03-12 三菱重工業株式会社 高圧蒸気加減弁
JPH05149472A (ja) * 1991-11-29 1993-06-15 Mitsubishi Heavy Ind Ltd ケージ型弁
JPH05187576A (ja) * 1992-01-08 1993-07-27 Ntc Kogyo Kk ゴム式流量調整弁
JPH0628438U (ja) * 1992-09-14 1994-04-15 株式会社キッツ 逆止め弁内蔵ボール弁
JPH06109164A (ja) * 1992-09-29 1994-04-19 Yamatake Honeywell Co Ltd アングル弁
JPH09133252A (ja) * 1995-11-10 1997-05-20 Mitsubishi Heavy Ind Ltd 大型蒸気加減弁
JP2002071241A (ja) * 2000-08-30 2002-03-08 Mitsubishi Heavy Ind Ltd 空調装置及びその冷媒制御用絞り弁
JP2006308274A (ja) * 2005-03-31 2006-11-09 Daikin Ind Ltd 膨張弁及び冷凍装置

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0519766U (ja) * 1991-08-30 1993-03-12 三菱重工業株式会社 高圧蒸気加減弁
JPH05149472A (ja) * 1991-11-29 1993-06-15 Mitsubishi Heavy Ind Ltd ケージ型弁
JPH05187576A (ja) * 1992-01-08 1993-07-27 Ntc Kogyo Kk ゴム式流量調整弁
JPH0628438U (ja) * 1992-09-14 1994-04-15 株式会社キッツ 逆止め弁内蔵ボール弁
JPH06109164A (ja) * 1992-09-29 1994-04-19 Yamatake Honeywell Co Ltd アングル弁
JPH09133252A (ja) * 1995-11-10 1997-05-20 Mitsubishi Heavy Ind Ltd 大型蒸気加減弁
JP2002071241A (ja) * 2000-08-30 2002-03-08 Mitsubishi Heavy Ind Ltd 空調装置及びその冷媒制御用絞り弁
JP2006308274A (ja) * 2005-03-31 2006-11-09 Daikin Ind Ltd 膨張弁及び冷凍装置

Also Published As

Publication number Publication date
CN204628600U (zh) 2015-09-09
WO2014061385A1 (fr) 2014-04-24

Similar Documents

Publication Publication Date Title
JP6091515B2 (ja) 絞り装置、および冷凍サイクル装置
WO2015015752A1 (fr) Éjecteur
JP2006266667A (ja) 膨張弁及び冷凍装置
US20110061423A1 (en) Ejector
JP2006275452A (ja) 膨張弁
CN106461092B (zh) 膨胀阀及制冷循环装置
JPWO2019058540A1 (ja) 冷媒分配器、及び、空気調和装置
JPWO2015045073A1 (ja) 積層型ヘッダー、熱交換器、及び、空気調和装置
JP2018194251A (ja) 熱交換器
JP5535098B2 (ja) 冷凍サイクル装置
WO2014061385A1 (fr) Dispositif d'étranglement, et dispositif de cycle frigorifique
JP2009121804A (ja) 蒸発器ユニット
JP2007032980A (ja) 膨張弁
JP5881845B2 (ja) 絞り装置、および冷凍サイクル装置
JP2004257727A (ja) 膨張弁
JP2005351605A (ja) 膨張弁及び冷凍装置
WO2014155816A1 (fr) Soupape de détente et dispositif de cycle de refroidissement utilisant celle-ci
JP5193630B2 (ja) 熱交換器
JP2013148284A (ja) 絞り装置およびその絞り装置を備えた空気調和装置
JP2008107054A (ja) 減圧装置および冷凍サイクル装置
WO2016143291A1 (fr) Éjecteur et cycle de réfrigération de type à éjecteur
JP6667070B2 (ja) 冷媒分流器およびそれを用いた冷凍システム
CN203550354U (zh) 节流装置及制冷循环装置
JP2002098443A (ja) 冷凍サイクル装置
WO2018131122A1 (fr) Détendeur et dispositif à cycle de réfrigération équipé de celui-ci

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12886903

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 12886903

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: JP