WO2014061056A1 - Restriction device, and refrigeration cycle device - Google Patents

Restriction device, and refrigeration cycle device Download PDF

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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
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WO
WIPO (PCT)
Prior art keywords
main body
valve
flow path
refrigerant
flow
Prior art date
Application number
PCT/JP2012/006613
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French (fr)
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/en
Priority to CN201390000811.0U priority patent/CN204628600U/en
Priority to JP2014542001A priority patent/JP5881845B2/en
Priority to PCT/JP2013/074860 priority patent/WO2014061385A1/en
Priority to CN201320634382.4U priority patent/CN203550354U/en
Publication of WO2014061056A1 publication Critical patent/WO2014061056A1/en

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    • 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.

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  • 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

The present invention is provided with: a main body (1) in which a first flow path (2) and a second flow path (3) are connected; a valve chamber (14) which is formed inside the main body (1), and which communicates with the first flow path (2); a valve seat (10) which is formed in the valve chamber (14), and which is provided with an opening that communicates with the second flow path (3); and a valve body (4) which is provided facing the opening of the valve seat (10) so as to be capable of advancing and retracting, and which adjusts the opening amount of the opening. In the main body (1), a plurality of main-body flow paths (13) communicating the second flow path (3) and the opening of the valve seat (10) are formed such that the flow directions in the plurality of main-body flow paths (13) form angles with the axial direction of the valve body (4).

Description

絞り装置、および冷凍サイクル装置Throttle device and refrigeration cycle device
　本発明は、流体の流量を調整する絞り装置、およびそれを備えた冷凍サイクル装置に関するものである。 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.
　流体（例えば冷媒）の流量を制御する絞り装置にあっては、弁体が装備されている弁室を冷媒が通過する際に流体音（冷媒音）を発生させる。気相と液相が共存する二相流で冷媒が弁室内に流入すると、弁体と弁室で形成される絞り部を、気相と液相が交互に不連続に通過するため圧力変動が生じ冷媒音が発生する場合がある。また絞り部の下流側は圧力低下しているため二相流であり、気泡の乱れや衝突により冷媒音が発生する場合がある。このような冷媒音を低減するために、従来より種々の工夫と提案がなされている。 In a throttling device that controls the flow rate of fluid (for example, refrigerant), fluid noise (refrigerant sound) is generated when the refrigerant passes through a valve chamber equipped with a valve element. When the refrigerant flows into the valve chamber in a two-phase flow in which the gas phase and the liquid phase coexist, 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. Further, since 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. In order to reduce such refrigerant noise, various devices and proposals have been conventionally made.
　そのような絞り装置の例として、複数の小孔を有する薄板部材を冷媒流れ経路に設けることで、二相冷媒中の気泡を細分化して冷媒音を低減させるものがある（例えば、特許文献１参照）。
　また、弁室に流路形状を設けて複数の流路を構成することで、冷媒噴流の運動エネルギーを低下させ圧力変動を小さくさせて、冷媒音を低減させるものがある（例えば、特許文献２参照）。
　また、弁室内に隔壁部材を装着し、この隔壁部材に流体入口側空間と流体出口側空間とを連通する連通路を設けたものがある（例えば、特許文献３参照）。 As an example of such 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).
In addition, 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).
In addition, there is a type in which 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).
特開２００７－１０７６２３号公報（段落［００１０］）JP 2007-107623 A (paragraph [0010]) 特開２００５－３５１６０５号公報（段落［００４７］、［００５３］）Japanese Patent Laying-Open No. 2005-351605 (paragraphs [0047] and [0053]) 特開２００６－２０７８５２号公報（段落［００３６］）JP 2006-207852 A (paragraph [0036])
　特許文献１～３に記載の技術は、流体の流れを１次元的に捉え、流体音を低減する対策を講じており、一旦複数の経路を通過してから集約することで、冷媒の流れを均質化しようとするが、複数の経路の流れ方向の影響について言及しておらず、流体音を低減する効果が少ない。複数の経路から集約して一つの流れとなるまでの過程に着目し、より流動音を抑制する対策が望まれている。 The technologies described in 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.
　本発明は、上記のような課題を解決するためになされたもので、絞り装置を流通する流体の流体音を抑制することができる絞り装置、およびそれを備えた冷凍サイクル装置を得るものである。 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. .
　本発明に係る絞り装置は、第１流路と第２流路とが接続される本体と、前記本体内部に形成され前記第１流路と連通する弁室と、前記弁室に形成され前記第２流路と連通する開口を有する弁座と、前記弁座の開口に向かって進退自在に設けられ、前記開口の開度を調節する弁体とを備え、前記本体は、前記第２流路と前記弁座の開口とを連通する複数の本体流路が形成され、前記複数の本体流路の流通方向が、前記弁体の軸方向と角度をなして形成されたものである。 A throttling device according to the present invention 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.
　本発明は、第２流路と弁座の開口とを連通する複数の本体流路を形成し、この複数の本体流路の流通方向が、弁体の軸方向と角度をなして形成されている。これにより、流体流れを効果的に分散させることで流体エネルギーを低減し、流体音を低減することができる。 In the present invention, 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. Thereby, fluid energy can be reduced by effectively dispersing the fluid flow, and fluid sound can be reduced.
本発明の実施の形態１における絞り装置の構成を示す図である。It is a figure which shows the structure of the aperture_diaphragm | restriction apparatus in Embodiment 1 of this invention. 本発明の実施の形態１における絞り装置の要部の断面図である。It is sectional drawing of the principal part of the aperture_diaphragm | restriction apparatus in Embodiment 1 of this invention. 図２におけるＡ－Ａ矢視断面図である。FIG. 3 is a cross-sectional view taken along line AA in FIG. 2. 図２におけるＢ－Ｂ矢視断面図である。FIG. 3 is a cross-sectional view taken along the line BB in FIG. 2. 本発明の実施の形態１における絞り装置の正方向流れ速度分布である。It is a forward direction flow velocity distribution of the throttle apparatus in Embodiment 1 of this invention. 本発明の実施の形態１における絞り装置の逆方向流れ速度分布である。It is a reverse direction flow velocity distribution of the diaphragm | throttle device in Embodiment 1 of this invention. 本発明の実施の形態１における絞り装置の複数の経路での効果を説明する概略図である。It is the schematic explaining the effect in the several path | route of the aperture_diaphragm | restriction apparatus in Embodiment 1 of this invention. 本発明の実施の形態１における絞り装置の要部の断面図である。It is sectional drawing of the principal part of the aperture_diaphragm | restriction apparatus in Embodiment 1 of this invention. 本発明の実施の形態１における絞り装置の他の構成例を示す図である。It is a figure which shows the other structural example of the aperture_diaphragm | restriction apparatus in Embodiment 1 of this invention. 絞り装置のよどみや渦の発生を説明する図である。It is a figure explaining generation | occurrence | production of stagnation and a vortex of a diaphragm | throttle device. 本発明の実施の形態２における絞り装置の要部の断面図である。It is sectional drawing of the principal part of the aperture_diaphragm | restriction apparatus in Embodiment 2 of this invention. 本発明の実施の形態３における冷凍サイクル装置の構成を示す図である。It is a figure which shows the structure of the refrigerating-cycle apparatus in Embodiment 3 of this invention. 従来の絞り装置の要部の断面図である。It is sectional drawing of the principal part of the conventional aperture_diaphragm | restriction apparatus. 従来の絞り装置の正方向流れ速度分布である。It is a forward direction flow velocity distribution of the conventional throttle device. 従来の絞り装置の逆方向流れ速度分布である。It is a reverse flow velocity distribution of the conventional throttle device.
　以下の実施の形態においては、冷凍サイクル装置において冷媒の流量を調整する絞り装置に、本発明を適用した場合を例に説明する。なお、本発明の絞り装置は冷媒の流量調節に限られるものではなく任意の流体に適用することができる。 In the following embodiments, 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.
実施の形態１．
　図１は、本発明の実施の形態１における絞り装置の構成を示す図である。
　図２は、本発明の実施の形態１における絞り装置の要部の断面図である。
　図３は、図２におけるＡ－Ａ矢視断面図である。
　図４は、図２におけるＢ－Ｂ矢視断面図である。
　なお、図２においては、絞り装置の開度が全閉の場合を示している。
　図に示すように、絞り装置１００は、第１流路２と第２流路３とが接続される本体１と、本体１内部に形成され第１流路２と連通する弁室１４と、弁室１４に形成され第２流路３と連通するオリフィス１１を有する弁座１０と、弁座１０のオリフィス１１に向かって進退自在に設けられ、オリフィス１１の開度を調節する弁体４とを備えている。
　なお、オリフィス１１は、本発明における「弁座の開口」に相当する。 Embodiment 1 FIG.
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.
As shown in the figure, 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.
　本体１は、例えば円筒形状を有している。第１流路２及び第２流路３は、冷媒配管により構成され、冷媒配管の先端が本体１の開口部に挿入され、ろう付け等の接合手段により固着される。第１流路２は、本体１の半径方向に設けられる。第２流路３は、本体１の軸線上に設けられる。つまり、第１流路２と第２流路３とは互いに直交する方向に設けられる。 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, and the front-end | tip of 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.
　また、弁体４の上部には、弁体４と図示しない移動機構を介して連結されたロータと、ステータとにより構成されるステッピングモータ２０を備えている。このステッピングモータ２０の回転が移動機構によって並進距離に変換され、弁体４が軸方向（上下方向）に移動して弁座１０の開口の開度を制御する。 Further, 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.
　弁体４は、弁室１４を貫通する弁体胴体部５と、弁座１０のオリフィス１１の開口よりも小径に形成された弁体先端部７と、弁体胴体部５と弁体先端部７とを接続するニードル部６とを有している。そして、弁体胴体部５の略中心軸上に、例えば円柱形状の弁体先端部７が形成されている。弁体４の弁体先端部７は本体軸受部９に回転かつ軸方向に移動可能に嵌合されている。なお、弁体胴体部５および弁体先端部７の形状は円柱に限定するものではない。 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. In addition, the shape of the valve body trunk | drum 5 and the valve body front-end | tip part 7 is not limited to a cylinder.
　本体１には、弁体４を支持する本体軸受部９が形成されている。本体軸受部９は、第２流路３とオリフィス１１とを連通し冷媒（流体）が流通する本体流路１３と、弁体先端部７が嵌入される弁体支持用孔１２とにより形成されている。弁体支持用孔１２は、弁体４の弁体先端部７の外径よりも、僅かに大きい内径を有する嵌入孔により形成されており、弁体４の弁体先端部７が摺動自在に挿入されることで、弁体先端部７と摺接して弁体４を支持する。 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. ing. 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.
　本体流路１３は、弁体先端部７の周囲に複数形成されている。この複数の本体流路１３は、それぞれ円形状に形成され、例えば図３、図４に示すように、オリフィス１１と同心円の円周上に略等間隔に配置されている。また、本体流路１３は、冷媒の流通方向が、弁体４の軸方向、即ち、第２流路３の軸方向と角度をなして形成されている。これにより本体流路１３は、オリフィス１１から第２流路３の外周方向へ向けて傾斜する流路を構成している。この複数の本体流路１３は、互いの間隔が、第２流路３側の間隔よりオリフィス１１側の間隔が狭く形成されている。すなわち、複数の本体流路１３の中心軸は、オリフィス１１側から第２流路３側に向かって、外側に広がるように形成されている。
　また、本体軸受部９は、オリフィス１１と間隔を空けて配置されており、この間隔によりオリフィス１１と本体軸受部９との間で複数の本体流路１３が連通している。 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. Thus, 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. That is, 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.
（冷媒の流れ）
　次に、絞り装置１００における冷媒の流れについて説明する。
　図２に示すように、全閉時には弁体４のニードル部６と弁座１０とが当接して密着状態で保持される。
　ステッピングモータ２０の回転により弁体４が上方に移動されると、弁体４は、上方へ移動する。これにより弁体４のニードル部６と弁座１０との間の流路面積が変化し、流量が調節される（１段目絞り）。このとき、第１流路２から第２流路３へ向かう冷媒は、オリフィス１１の出口側から各本体流路１３に分流して第２流路３へと至る。また、第２流路３から第１流路２へ向かう冷媒は、複数の本体流路１３に分流されたあと、本体軸受部９とオリフィス１１との間で再び合流し、オリフィス１１へと至る。
　そして、さらに弁体４を上方に移動させ、弁体４のニードル部６と弁座１０との間の流路面積が最大とした場合（全開開度）においては、オリフィス１１によって流量が制限される（２段目絞り）。
　また、ステッピングモータ２０の回転により弁体４が下方に移動されると、弁体４は下方へ摺動移動する。そして、弁体４のニードル部６と弁座１０とが当接して密着状態で保持することで全閉状態となる。 (Refrigerant flow)
Next, the flow of the refrigerant in the expansion device 100 will be described.
As shown in FIG. 2, when fully closed, the needle portion 6 of the valve body 4 and the valve seat 10 come into contact with each other and are held in close contact.
When the valve body 4 is moved upward by the rotation of the stepping motor 20, the valve body 4 is moved upward. Thereby, the flow path area between the needle part 6 of the valve body 4 and the valve seat 10 changes, and the flow rate is adjusted (first stage restriction). At this time, the refrigerant traveling from the first flow path 2 to the second flow path 3 is diverted to the main flow paths 13 from the outlet side of the orifice 11 and reaches the second flow path 3. In addition, 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. .
Further, when 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).
Further, when the valve body 4 is moved downward by the rotation of the stepping motor 20, the valve body 4 slides downward. And the needle part 6 and the valve seat 10 of the valve body 4 contact | abut and hold | maintain in a close contact state, and it will be in a fully closed state.
　絞り装置１００に流入する冷媒は、液相冷媒中に気相冷媒が泡沫として混入することがある。この気液混合冷媒が絞り装置１００を通過する際に騒音の原因となる。騒音の主な要因は、気相冷媒の泡沫の存在であることが判明しており、特に大きな泡沫の存在が問題となる。
　まず本実施の形態における冷媒音対策を説明する前に、従来事例をもとに課題を説明する。 As for the refrigerant flowing into the expansion device 100, the gas-phase refrigerant may be mixed in the liquid-phase refrigerant as foam. When 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.
First, before describing countermeasures against refrigerant noise in the present embodiment, problems will be described based on conventional examples.
（従来事例）
　図１３は、従来の絞り装置の要部の断面図である。図１３においては、絞り装置の開度が全閉の場合を示している。
　図１３に示すように、従来事例の絞り装置では、本発明の実施の形態１と比較して、弁体先端部７、本体軸受部９、弁体支持用孔１２、複数の本体流路１３が設けられていない。
　この従来事例の絞り装置において、第１流路２から第２流路３へ冷媒が流れる方向を、正方向流れとし、第２流路３から第１流路２へ冷媒が流れる方向を逆方向流れとする。
　そして、この従来事例の絞り装置において、正方向流れ、および逆方向流れについて、所定の開度、所定の差圧が与えられた場合の平均速度場の解析結果を図１４、図１５に示す。 (Conventional example)
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.
As shown in FIG. 13, in the throttle device of the conventional example, compared with the first embodiment of the present invention, 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.
In this conventional throttle device, the direction in which the refrigerant flows from the first flow path 2 to the second flow path 3 is the forward flow, and 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.
　図１４は、従来の絞り装置の正方向流れ速度分布である。
　図１４に示すように、第１流路２や弁室１４では冷媒の速度は低い。ニードル部６と弁座１０との間の狭い領域の流路で冷媒の速度が高くなり、ニードル部６に沿って円錐状に狭まるように流れる。この狭い領域を出ると第２流路３内に入るが、慣性があるので円錐状に狭まるように流れる。その結果運動エネルギーが集約し、冷媒速度が高くなる。また、オリフィス１１のある箇所で圧力変動があると、それが他の冷媒流れに与える影響は、それぞれの流れが集約する方向なので、非常に大きい。オリフィス１１を中心として、第２流路３で、冷媒速度が非常に高い。 FIG. 14 is a forward flow velocity distribution of a conventional throttle device.
As shown in FIG. 14, 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. When exiting this narrow region, it enters the second flow path 3 but flows so as to narrow in a conical shape due to inertia. As a result, kinetic energy is concentrated and the refrigerant speed is increased. In addition, if there is a pressure fluctuation at a position where the orifice 11 is present, 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.
　図１５は、従来の絞り装置の逆方向流れ速度分布である。
　図１５に示すように、ほとんどの領域で冷媒の速度が低い。第２流路３やオリフィスでは冷媒速度が小さい。ニードル部６と弁座１０との間の狭い領域の流路で冷媒の速度が高くなり、ニードル部６に沿って円錐状に広がるように流れる。この狭い領域を出ると弁室１４内に入るが、慣性があるので円錐状に広がるように流れる。その結果運動エネルギーが拡散するので、冷媒速度が低い。また、弁室１４のある箇所で圧力変動があったとしても、それが他の冷媒流れに与える影響は、それぞれの流れが離れていく方向なので、小さい。 FIG. 15 is a reverse flow velocity distribution of the conventional throttle device.
As shown in FIG. 15, 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.
　以上より、図１４に示す正方向流れより、図１５に示す逆方向流れの方が、冷媒速度が高くなる領域が少なく、冷媒音が低いように窺える。実際に観測した結果でも、正方向流れより逆方向流れの方が、冷媒音が小さい。つまり、冷媒音を抑制するには、図１５の流体の流れのように、絞り装置内部の流体の流れを、進行方向に対して広がるような流れにすればよい。 From the above, 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.
（本実施の形態での冷媒流れ）
　次に、本実施の形態１での冷媒流れについて説明する。
　本実施の形態１の絞り装置１００においても、第１流路２から第２流路３へ冷媒が流れる方向を、正方向流れとし、第２流路３から第１流路２へ冷媒が流れる方向を逆方向流れとする。
　本実施の形態１の絞り装置１００において、正方向流れ、および逆方向流れについて、所定の開度、所定の差圧が与えられた場合の平均速度場の解析結果を図５、図６に示す。 (Refrigerant flow in the present embodiment)
Next, the refrigerant flow in the first embodiment will be described.
Also in the expansion device 100 of the first embodiment, the direction in which the refrigerant flows from the first flow path 2 to the second flow path 3 is the forward flow, and the refrigerant flows from the second flow path 3 to the first flow path 2. The direction is the reverse flow.
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. .
　図５は、本発明の実施の形態１における絞り装置の正方向流れ速度分布である。
　図５に示すように、ほとんどの領域で冷媒の速度が低い。第１流路２や弁室１４では冷媒の速度は低い。ニードル部６と弁座１０との間の狭い領域の流路で冷媒の速度が高くなり、ニードル部６に沿って円錐状に狭まるように流れる。この狭い領域を出ると、慣性があるので円錐状に狭まるように流れようとする。しかし、弁体先端部７があるため、流れが中央に集約することがない。さらには、複数の本体流路１３を通過することで、流れが分割され、かつ分散する方向に冷媒が流れる。 FIG. 5 is a forward flow velocity distribution of the throttle device according to Embodiment 1 of the present invention.
As shown in FIG. 5, the refrigerant speed is low in most regions. In the first flow path 2 and the valve chamber 14, 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. When leaving this narrow area, there is inertia, so it tends to flow in a conical shape. However, since the valve body tip portion 7 is present, the flow is not concentrated in the center. Furthermore, 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.
　また、オリフィス１１のある箇所で圧力変動があると、それが他の冷媒流れに与える影響が存在するが、オリフィス１１の径に比べて十分短い経路を通過すると、複数の本体流路１３に至るので、圧力変動が互いに影響を与えることがない。複数の本体流路１３内では、当然ながら圧力変動が互いに影響を与えることがない。
　このように、図５に示す実施の形態１における絞り装置１００の正方向流れでは、図１４に示した従来の絞り装置の正方向流れと比較して、冷媒速度が高くなる領域が少なく、冷媒音が抑制される。 Further, if there is a pressure fluctuation at a location where the orifice 11 is present, this has an effect on other refrigerant flows. However, if a passage sufficiently shorter than the diameter of the orifice 11 is passed, a plurality of main body flow paths 13 are reached. Therefore, pressure fluctuations do not affect each other. Of course, pressure fluctuations do not affect each other in the plurality of main body flow paths 13.
Thus, in the forward direction flow of the expansion device 100 in the first embodiment shown in FIG. 5, the region in which the refrigerant speed is high is smaller than the forward direction flow of the conventional expansion device shown in FIG. Sound is suppressed.
　図６は、本発明の実施の形態１における絞り装置の逆方向流れ速度分布である。
　図６に示すように、ほとんどの領域で冷媒の速度が低い。第２流路３、複数の本体流路１３、オリフィス１１では冷媒速度が小さい。ニードル部６と弁座１０との間の狭い領域の流路で冷媒の速度が高くなり、ニードル部６に沿って円錐状に広がるように流れる。この狭い領域を出ると弁室１４内に入るが、慣性があるので円錐状に広がるように流れる。その結果運動エネルギーが拡散するので、冷媒速度が低い。また弁室１４のある箇所で圧力変動があったとしても、それが他の冷媒流れに与える影響は、それぞれの流れが離れていく方向なので小さい。このように、図６に示す実施の形態１における絞り装置１００の逆方向流れでは、図１５に示した従来の絞り装置の逆方向流れと略同様の平均速度場となる。 FIG. 6 is a reverse flow velocity distribution of the throttle device according to Embodiment 1 of the present invention.
As shown in FIG. 6, the refrigerant speed is low in most regions. In the second flow path 3, the plurality of main body flow paths 13, and the orifice 11, the refrigerant speed 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 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. Moreover, even if there is a pressure fluctuation at a certain location of the valve chamber 14, the influence on the other refrigerant flows is small because each flow is away. Thus, 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.
　以上のように、本実施の形態１における絞り装置１００は、オリフィス１１と第２流路３との間に、オリフィス１１と第２流路３とを連通する複数の本体流路１３が形成されている。このため、冷媒流れを効果的に分散させることで流体エネルギーを低減し、冷媒速度が高くなる領域を少なくすることができ、圧力変動の増加を抑制でき、冷媒音（流体音）を低減することができる。 As described above, in the expansion device 100 according to the first embodiment, 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.
（複数の本体流路１３の流路面積）
　本実施の形態１における絞り装置１００は、図４に示すように、複数の本体流路１３の流路面積の総計が、オリフィス１１の流路面積より大きく形成されている。
　そのため、オリフィス１１の開度が全閉から全開まで変化しても、複数の本体流路１３が流量を決定する主要因とならない。よって、例えば、複数の本体流路１３を設けた本実施の形態１の絞り装置１００と、複数の本体流路１３を設けていない従来の絞り装置とが、同一の冷凍サイクル装置内に共存するとしても、流量特性がほぼ共通化できるため、製造コストが低減できる。 (Flow path area of the plurality of main body flow paths 13)
As shown in FIG. 4, 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.
（複数の本体流路１３の流路長さ）
　図７は、本発明の実施の形態１における絞り装置の複数の経路での効果を説明する概略図である。
　図７（ａ）は、従来の絞り装置を示し、複数の本体流路１３の流路長さＬａが、複数の本体流路１３の最近接距離Ｄａより短い場合（Ｄａ＞Ｌａ）を示している。
　図７（ｂ）は、本実施の形態１の絞り装置１００を示し、複数の本体流路１３の流路長さＬｂが、複数の本体流路１３の最近接距離Ｄｂより長い場合（Ｄｂ＜Ｌｂ）を示している。 (Flow path length of the plurality of main body flow paths 13)
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). Yes.
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).
　図７（ａ）に示すように、複数の本体流路１３の流路長さが最接近距離より短いと、複数の本体流路１３を出た後の冷媒流れは直進性が低く、広がりながら冷媒が流れようとする。
　一方、図７（ｂ）に示すように、複数の本体流路１３の流路長さが最接近距離より長いと、複数の本体流路１３を出た後の冷媒流れは直進性が高く、隣り合う複数の本体流路１３同士の冷媒流れが混じり合うまでに進む距離が、図７（ａ）と比較して長くなる。
　このように、隣り合う複数の本体流路１３同士の冷媒流れが混じり合うまでに進む距離の間は、分散流れのために速度が低下するため、冷媒流れが混じり合った後に圧力変動に与える影響が小さくなる。よって、より冷媒音の抑制効果を得ることができる。 As shown in FIG. 7A, when the flow path lengths of the plurality of main body flow paths 13 are shorter than the closest approach distance, the refrigerant flow after exiting the plurality of main body flow paths 13 is low in straightness and spreading. The refrigerant is about to flow.
On the other hand, as shown in FIG. 7 (b), when the flow lengths of the plurality of main body flow paths 13 are longer than the closest distance, the refrigerant flow after exiting the plurality of main body flow paths 13 has high straightness, The distance traveled until the refrigerant flows of the plurality of adjacent main body flow paths 13 are mixed is longer than that in FIG.
In this way, during the distance traveled until the refrigerant flows of the plurality of adjacent main body flow paths 13 are mixed, the speed decreases due to the dispersed flow, and therefore the influence on the pressure fluctuation after the refrigerant flows are mixed. Becomes smaller. Therefore, the effect of suppressing the refrigerant noise can be obtained.
（複数の本体流路１３のオリフィス１１までの距離）
　図８は、本発明の実施の形態１における絞り装置の要部の断面図である。
　図８に示すように、本実施の形態１における絞り装置１００は、複数の本体流路１３のオリフィス１１側の端部から弁座１０までの距離Ｗが、オリフィス１１の開口幅Ｒより小さく形成されている。
　距離Ｗが長くなると、弁体４のニードル部６に沿って円錐状に狭まるように流れた冷媒が中央に集約し、または乱れを発生し、冷媒速度の分布変動や圧力変動が生じて冷媒音を生じさせる。
　本実施の形態１では、距離Ｗを開口幅Ｒより小さくしているので、複数の本体流路１３のオリフィス１１側の端部から弁座１０までの間の冷媒流れの集約や乱れを抑制でき、より冷媒音を抑制することができる。 (Distance to the orifices 11 of the plurality of main body flow paths 13)
FIG. 8 is a cross-sectional view of a main part of the diaphragm device according to Embodiment 1 of the present invention.
As shown in FIG. 8, 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.
When the distance W is increased, 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. Give rise to
In the first embodiment, since 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. Thus, refrigerant noise can be further suppressed.
（絞り装置１００の他の構成例）
　図９は、本発明の実施の形態１における絞り装置の他の構成例を示す図である。
　図９に示すように、弁体先端部７、本体軸受部９、弁体支持用孔１２を省略し、中央部１７の周囲に複数の本体流路１３を形成するようにしても良い。このような構成においても、上述した効果を奏することができる。 (Other configuration examples of the diaphragm device 100)
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.
　なお、本実施の形態１では、本体１に複数の本体流路１３を形成する場合を説明したが、本発明はこれに限らず、本体１とは別体で形成しても良い。例えば、円柱状の部材に複数の本体流路１３を形成し、この円柱状の部材を、オリフィス１１の第２流路３側に距離Ｗを隔てて配置するようにしても良い。 In the first embodiment, the case where a plurality of main body flow paths 13 are formed in the main body 1 has been described. However, the present invention is not limited to this and may be formed separately from the main body 1. For example, 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.
実施の形態２．
　図１０は、絞り装置のよどみや渦の発生を説明する図である。
　図１０に示すように、複数の本体流路１３を通過した冷媒が第２流路３内へ流出すると、冷媒流れのよどみや渦が発生する場合がある。このような冷媒流れのよどみや渦は、冷媒音の原因となる場合がある。 Embodiment 2. 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.
　図１１は、本発明の実施の形態２における絞り装置の要部の断面図である。
　図１１に示すように、本発明の実施の形態２における絞り装置１００は、上記実施の形態１の構成に加え、本体軸受部９（中央部）の第２流路３側に、本体軸受部９（中央部）から第２流路３に延出する静止部材１５を設けている。
　これにより、複数の本体流路１３を通過した冷媒は、静止部材１５と第２流路３の内壁との間の流路に沿って流れ、冷媒流れのよどみや渦の発生を抑制できる。よって、冷媒音を抑制することができる。
　なお、図１１に示すように、静止部材１５の形状は、複数の本体流路１３の流通方向に沿うように、本体軸受部９の端部から第２流路３側に拡径する円錐形状を有し、第２流路３の内壁側を流通した冷媒が拡散するように、第２流路３の内壁と所定間隔を隔てたあと縮径する円錐形状を有する。 FIG. 11 is a cross-sectional view of a main part of the diaphragm device according to Embodiment 2 of the present invention.
As shown in FIG. 11, in addition to the configuration of the first embodiment, 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.
As shown in FIG. 11, 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.
実施の形態３．
（空気調和装置）
　上記実施の形態１、２の絞り装置１００を備えた空気調和装置について説明する。
　図１２は、本発明の実施の形態３における冷凍サイクル装置の構成を示す図である。
　図１２に示すように、冷凍サイクル装置は、圧縮機１１０、凝縮器１２０、絞り装置１００、および蒸発器１３０を備え、順次、冷媒配管で接続されて冷媒回路を構成している。 Embodiment 3 FIG.
(Air conditioner)
The air conditioner provided with the expansion device 100 of the first and second embodiments will be described.
FIG. 12 is a diagram illustrating a configuration of the refrigeration cycle apparatus according to Embodiment 3 of the present invention.
As shown in FIG. 12, 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.
　圧縮機１１０は冷媒を圧縮し、凝縮器１２０に流入させる。凝縮器１２０は、圧縮機１１０によって圧縮された冷媒を凝縮する。絞り装置１００は、第１流路２を構成する冷媒配管により、凝縮器１２０と接続され、凝縮器１２０によって凝縮された冷媒を膨張する。また、絞り装置１００は、第２流路３を構成する冷媒配管により、蒸発器１３０と接続されている。蒸発器１３０は、絞り装置１００によって膨張された冷媒を蒸発する。 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.
　このような構成において、圧縮機１１０を起動すると、低圧のガス冷媒は、圧縮機１１０に吸入されて圧縮されて高圧のガス冷媒となる。高圧のガス冷媒は、凝縮器１２０で凝縮されて高圧の液冷媒となる。そして、この高圧の液冷媒は、絞り装置１００によって減圧されて、低温低圧の気液二相冷媒となり、蒸発器１３０で蒸発されて低圧のガス冷媒となる。この低圧のガス冷媒は、再び圧縮機１１０に吸入される。
　この冷凍サイクル装置は、例えば空気調和装置等に用いることができ、凝縮器１２０での発熱を利用して暖房を行う。また、蒸発器１３０の吸熱を利用して冷房を行う。
　なお、絞り装置１００の第１流路２を構成する冷媒配管に蒸発器１３０を接続し、第２流路３を構成する冷媒配管に凝縮器１２０を接続するようにしても良い。また、四方弁を設けて冷媒の循環方向を変えることにより、冷房・暖房運転の切り替えを行うようにしても良い。 In such a configuration, 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.
Note that 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.
　以上のように、本実施の形態３における冷凍サイクル装置は、冷媒音を抑制することが可能である。特に、絞り装置１００を負荷側（室内側）に配置した場合には、室内の人に冷媒音を聞こえにくくすることができ、快適性を向上することができる。 As described above, the refrigeration cycle apparatus according to Embodiment 3 can suppress refrigerant noise. In particular, when 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.
　１　本体、２　第１流路、３　第２流路、４　弁体、５　弁体胴体部、６　ニードル部、７　弁体先端部、９　本体軸受部、１０　弁座、１１　オリフィス、１２　弁体支持用孔、１３　本体流路、１４　弁室、１５　静止部材、１７　中央部、２０　ステッピングモータ、１００　絞り装置、１１０　圧縮機、１２０　凝縮器、１３０　蒸発器、２００　冷凍サイクル装置。 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.

Claims (8)

  1. 　第１流路と第２流路とが接続される本体と、
    　前記本体内部に形成され前記第１流路と連通する弁室と、
    　前記弁室に形成され前記第２流路と連通する開口を有する弁座と、
    　前記弁座の開口に向かって進退自在に設けられ、前記開口の開度を調節する弁体と
    を備え、
    　前記本体は、
    　前記第２流路と前記弁座の開口とを連通する複数の本体流路が形成され、
    　前記複数の本体流路の流通方向が、前記弁体の軸方向と角度をなして形成された
    ことを特徴とする絞り装置。     A main body to which the first flow path and the second flow path are connected;
    A valve chamber formed inside the main body and communicating with the first flow path;
    A valve seat formed in the valve chamber and having an opening communicating with the second flow path;
    A valve body that is provided so as to freely advance and retract toward the opening of the valve seat, and that adjusts the opening of the opening;
    The body is
    A plurality of main body flow paths communicating the second flow path and the opening of the valve seat are formed,
    2. A throttling device according to claim 1, wherein a flow direction of the plurality of main body flow paths is formed at an angle with an axial direction of the valve body.
  2. 　前記複数の本体流路は、
    　互いの間隔が、前記第２流路側の間隔より前記弁座の開口側の間隔が狭く形成された
    ことを特徴とする請求項１記載の絞り装置。     The plurality of main body channels are:
    2. A throttling device according to claim 1, wherein the interval between the valve passages is narrower than the interval on the second flow path side.
  3. 　前記複数の本体流路の開口面積の和が、前記弁座の開口の開口面積より大きい
    ことを特徴とする請求項１又は２記載の絞り装置。     3. A throttling device according to claim 1, wherein a sum of opening areas of the plurality of main body flow paths is larger than an opening area of the opening of the valve seat.
  4. 　前記複数の本体流路の前記弁座側の端部から前記弁座までの距離が、前記弁座の開口の開口幅より小さい
    ことを特徴とする請求項１～３の何れか一項に記載の絞り装置。     The distance from the valve seat side end of the plurality of main body flow paths to the valve seat is smaller than the opening width of the opening of the valve seat. Squeezing device.
  5. 　前記複数の本体流路の流路長さは、
    　当該複数の本体流路の互いの間隔より大きい
    ことを特徴とする請求項１～４の何れか一項に記載の絞り装置。     The channel lengths of the plurality of main body channels are:
    5. The expansion device according to claim 1, wherein the expansion device is larger than the interval between the plurality of main body flow paths.
  6. 　前記本体は、前記複数の本体流路が、前記弁体の中心軸上の中央部の周囲に形成され、
    　前記中央部の前記第２流路側に、前記中央部から前記第２流路に延出する静止部材を設けた
    ことを特徴とする請求項１～５の何れか一項に記載の絞り装置。     In the main body, the plurality of main body flow paths are formed around a central portion on a central axis of the valve body,
    The aperture device according to any one of claims 1 to 5, wherein a stationary member extending from the central part to the second flow path is provided on the second flow path side of the central part.
  7. 　前記弁体は、円柱状に形成され、
    　前記弁座の開口よりも大径に形成された弁体胴体部と、
    　前記弁座の開口よりも小径に形成された弁体先端部と、
    　前記弁体胴体部と前記弁体先端部とを接続するニードル部とを有し、
    　前記本体は、前記弁体先端部が嵌入される弁体支持用孔とが形成され、前記弁体支持用孔が前記弁体先端部と摺接して前記弁体を支持する本体軸受部を有し、
    　前記複数の本体流路は、前記本体軸受部の周囲に形成された
    ことを特徴とする請求項１～６の何れか一項に記載の絞り装置。     The valve body is formed in a cylindrical shape,
    A valve body body formed larger in diameter than the opening of the valve seat;
    A valve body tip formed with a smaller diameter than the opening of the valve seat;
    A needle part connecting the valve body body part and the valve body tip part,
    The main body has a valve body support hole into which the valve body tip portion is inserted, and the valve body support hole has a main body bearing portion that slidably contacts the valve body tip portion to support the valve body. And
    The throttle device according to any one of claims 1 to 6, wherein the plurality of main body flow paths are formed around the main body bearing portion.
  8. 　冷媒を圧縮する圧縮機と、
    　前記圧縮機によって圧縮された冷媒を凝縮する凝縮器と、
    　前記凝縮器によって凝縮された冷媒を膨張する、請求項１～７の何れか一項に記載の絞り装置と、
    　前記絞り装置によって膨張された冷媒を蒸発する蒸発器とを備えた
    ことを特徴とする冷凍サイクル装置。     A compressor for compressing the refrigerant;
    A condenser for condensing the refrigerant compressed by the compressor;
    The expansion device according to any one of claims 1 to 7, which expands the refrigerant condensed by the condenser;
    An refrigeration cycle apparatus comprising: an evaporator for evaporating the refrigerant expanded by the expansion device.
PCT/JP2012/006613 2012-10-16 2012-10-16 Restriction device, and refrigeration cycle device WO2014061056A1 (en)

Priority Applications (5)

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PCT/JP2012/006613 WO2014061056A1 (en) 2012-10-16 2012-10-16 Restriction device, and refrigeration cycle device
CN201390000811.0U CN204628600U (en) 2012-10-16 2013-09-13 Throttling arrangement and refrigerating circulatory device
JP2014542001A JP5881845B2 (en) 2012-10-16 2013-09-13 Throttle device and refrigeration cycle device
PCT/JP2013/074860 WO2014061385A1 (en) 2012-10-16 2013-09-13 Restriction device, and refrigeration cycle device
CN201320634382.4U CN203550354U (en) 2012-10-16 2013-10-15 Throttling device and refrigerating cycle device

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JP6910159B2 (en) * 2017-02-24 2021-07-28 三菱電機株式会社 Cooking device
CN114251462A (en) * 2020-09-24 2022-03-29 浙江盾安人工环境股份有限公司 Electronic expansion valve

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0519766U (en) * 1991-08-30 1993-03-12 三菱重工業株式会社 High pressure steam control valve
JPH05149472A (en) * 1991-11-29 1993-06-15 Mitsubishi Heavy Ind Ltd Cage type valve
JPH05187576A (en) * 1992-01-08 1993-07-27 Ntc Kogyo Kk Rubber type flow rate regulating valve
JPH0628438U (en) * 1992-09-14 1994-04-15 株式会社キッツ Check valve built-in ball valve
JPH06109164A (en) * 1992-09-29 1994-04-19 Yamatake Honeywell Co Ltd Angle valve
JPH09133252A (en) * 1995-11-10 1997-05-20 Mitsubishi Heavy Ind Ltd Large steam control valve
JP2002071241A (en) * 2000-08-30 2002-03-08 Mitsubishi Heavy Ind Ltd Air conditioner and its throttle valve for controlling refrigerant
JP2006308274A (en) * 2005-03-31 2006-11-09 Daikin Ind Ltd Expansion valve and refrigeration device

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0519766U (en) * 1991-08-30 1993-03-12 三菱重工業株式会社 High pressure steam control valve
JPH05149472A (en) * 1991-11-29 1993-06-15 Mitsubishi Heavy Ind Ltd Cage type valve
JPH05187576A (en) * 1992-01-08 1993-07-27 Ntc Kogyo Kk Rubber type flow rate regulating valve
JPH0628438U (en) * 1992-09-14 1994-04-15 株式会社キッツ Check valve built-in ball valve
JPH06109164A (en) * 1992-09-29 1994-04-19 Yamatake Honeywell Co Ltd Angle valve
JPH09133252A (en) * 1995-11-10 1997-05-20 Mitsubishi Heavy Ind Ltd Large steam control valve
JP2002071241A (en) * 2000-08-30 2002-03-08 Mitsubishi Heavy Ind Ltd Air conditioner and its throttle valve for controlling refrigerant
JP2006308274A (en) * 2005-03-31 2006-11-09 Daikin Ind Ltd Expansion valve and refrigeration device

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