WO2018062376A1 - 電動弁 - Google Patents

電動弁 Download PDF

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Publication number
WO2018062376A1
WO2018062376A1 PCT/JP2017/035189 JP2017035189W WO2018062376A1 WO 2018062376 A1 WO2018062376 A1 WO 2018062376A1 JP 2017035189 W JP2017035189 W JP 2017035189W WO 2018062376 A1 WO2018062376 A1 WO 2018062376A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
taper
motor
operated
operated valve
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2017/035189
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
大樹 中川
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Saginomiya Seisakusho Inc
Original Assignee
Saginomiya Seisakusho Inc
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 Saginomiya Seisakusho Inc filed Critical Saginomiya Seisakusho Inc
Priority to CN202110754553.6A priority Critical patent/CN113418014B/zh
Priority to JP2018542848A priority patent/JP6904968B2/ja
Priority to CN202110756179.3A priority patent/CN113324054B/zh
Priority to CN201780055963.3A priority patent/CN109715997B/zh
Publication of WO2018062376A1 publication Critical patent/WO2018062376A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16K1/36—Valve members
    • F16K1/38—Valve members of conical shape
    • 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
    • F16K1/52—Means for additional adjustment of the rate of flow
    • 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
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • 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 an electric valve used in a refrigeration cycle system or the like.
  • Patent Document 1 motor-operated valves used for package air conditioners, room air conditioners, refrigerators, and the like are known (for example, Patent Document 1).
  • this electric valve 100 for example, as shown in FIG. 7, when the stepping motor is driven and the rotor 103 rotates, the valve body 114 moves in the direction of the central axis L ′ by the screw feeding action of the female screw 131a and the male screw 121a. To do. Thereby, adjustment which opens and closes the valve port 121 is made, and the flow rate of the refrigerant flowing in from the pipe joint 111 and flowing out from the pipe joint 112 is controlled.
  • the first taper 114a seated on the valve seat 120 and the third taper 114c are relatively large.
  • FIG. 8B is a graph showing the flow rate characteristics of the motor-operated valve 100 in the low opening range.
  • the horizontal axis of the graph represents the amount of pulse applied to the stepping motor to move the valve body 114
  • the vertical axis of the graph represents the flow rate.
  • the origin of the graph represents the valve closed state at the time of 0 pulse.
  • a broken line A in the figure represents a change in flow rate when the valve body 114 is used.
  • a fold line B representing a change in flow rate when using a valve body 114 ′ in which the second taper 114 b is not formed as shown in FIG. 9 is shown as being proportional to the fold line A. .
  • the broken line B rapidly changes from the rising flow area 201 determined by the first taper 114′a to the flow area 203 determined by the third taper 114′c.
  • the flow rate characteristic is rapidly increased in the low opening range because the second taper 114b having a small angle controls the flow rate increase rate in the flow rate region 202 for a while. It can suppress changing.
  • FIG. 11A it is conceivable to reduce the rising flow rate by bringing the diameter D1 of the boundary between the first taper 314a and the second taper 314b closer to the inner diameter D2 of the valve seat 320.
  • the second taper 314b that controls the flow rate due to variations in processing of the valve body 314.
  • the valve body 314 bites into the valve seat 320 as described above.
  • a corner R315 is actually formed at such a boundary during processing, when the valve body 314 is seated on the valve seat 320, the portion of the corner R315 may come into contact with the valve seat 320. . Since the size and shape of the corner R315 are likely to vary in processing of the valve body 314, when the corner R315 contacts the valve seat 320 during seating, the rising flow rate characteristic differs for each motor-operated valve. Problems can occur.
  • An object of the present invention is to provide a motor-operated valve that can accurately control a minute flow rate in a low opening range.
  • the motor operated valve of the present invention is This is an electric valve that converts the rotational motion of the rotor into a linear motion by screwing the male screw member and the female screw member, and moves the valve element accommodated in the valve body in the axial direction based on this linear motion.
  • the valve body is A first taper abutting against the seating portion in the valve closed state; A second taper positioned ahead of the first taper; In a state where the first taper is in contact with the seating portion, a space wider than the clearance width formed between the valve port and the second taper is a width of the seating portion and the clearance. It is characterized by being formed between.
  • the first taper function is limited to the seating function as much as possible, the flow rate can be controlled mainly by the second taper, and the minute flow rate in the low opening range can be accurately controlled.
  • the motor operated valve of the present invention is On the rotor side of the valve port, a receding region that recedes from the valve body side is formed, In the valve closed state, the first taper abuts on the rotor-side edge of the retracted region as a seating portion, The space is formed between the receding region and the first taper in contact with the edge.
  • the motor operated valve of the present invention is The second taper is formed so that a height thereof is higher than a height of the receding region.
  • the motor operated valve of the present invention is The receding region is a chamfer that widens toward the rotor side.
  • the motor operated valve of the present invention is The taper angle of the tapered surface of the first taper with respect to the central axis of the valve body is larger than the inclination angle of the chamfered surface with respect to the central axis of the motor-operated valve.
  • the motor operated valve of the present invention is The receding region is a notch formed on the rotor side of the valve port.
  • the motor operated valve of the present invention is A constriction is formed between the first taper and the second taper; The space is formed between the constriction and the valve port in a state where the first taper is in contact with the seating portion.
  • FIG. 1 is a cross-sectional view showing an electric valve 2 according to an embodiment.
  • “upper” or “lower” is defined in the state of FIG. That is, the rotor 4 is positioned above the valve body 17.
  • the “height” in the present specification is also defined in the state of FIG. That is, the “height” indicates the length in the vertical direction in FIG.
  • valve main body 30 is integrally connected to the lower side of the opening side of the case 60 made of a non-magnetic material and having a cylindrical cup shape by welding or the like.
  • valve body 30 is made of a metal such as stainless steel and has the valve chamber 11 therein.
  • the valve body 30 is fixedly mounted with a first pipe joint 12 made of stainless steel or copper that communicates directly with the valve chamber 11.
  • a valve seat member 30 ⁇ / b> A in which a valve port 16 having a circular cross section is formed is provided on the lower inner side of the valve body 30.
  • a second pipe joint 15 made of stainless steel or copper, etc., communicating with the valve chamber 11 via the valve port 16 is fixedly attached to the valve seat member 30A.
  • Rotating rotor 4 is accommodated in the inner periphery of case 60, and valve shaft 41 is disposed on the shaft core portion of rotor 4 via a bush member (not shown).
  • the valve shaft 41 and the rotor 4 coupled by the bush member move integrally in the vertical direction while rotating.
  • a male screw 41 a is formed on the outer peripheral surface near the middle portion of the valve shaft 41.
  • the valve shaft 41 functions as a male screw member.
  • a stator made up of a yoke, bobbin, and coil (not shown) is disposed on the outer periphery of the case 60, and the rotor 4 and the stator constitute a stepping motor.
  • a guide support 52 is fixed to the ceiling surface of the case 60.
  • the guide support body 52 has a cylindrical portion 53 and an umbrella-shaped portion 54 formed on the upper end side of the cylindrical portion 53.
  • the entire guide support body 52 is integrally formed by press working.
  • the umbrella-shaped portion 54 is molded in substantially the same shape as the inside of the top portion of the case 60.
  • a cylindrical member 65 that also serves as a guide for the valve shaft 41 is fitted in the cylindrical portion 53 of the guide support 52.
  • the cylindrical member 65 is made of a material containing a lubricant or a surface-treated member made of metal or synthetic resin, and rotatably holds the valve shaft 41.
  • valve shaft holder 6 that has a function of forming a screw thread A with the valve shaft 41 and suppressing the inclination of the valve shaft 41, as will be described later, with respect to the valve body 30. It is fixed relatively unrotatable.
  • valve shaft holder 6 is fixed to the valve main body 30 by welding or the like, and a through hole 6h is formed inside the valve shaft holder 6.
  • a female screw 6d is formed downward from the upper opening 6g of the valve shaft holder 6 to a predetermined depth. For this reason, in this embodiment, the valve shaft holder 6 functions as a female screw member.
  • a screw thread A shown in FIG. 1 is constituted by a male screw 41 a formed on the outer periphery of the valve shaft 41 and a female screw 6 d formed on the inner periphery of the valve shaft holder 6.
  • a cylindrical valve guide 18 is disposed below the valve shaft 41 so as to be slidable with respect to the through hole 6 h of the valve shaft holder 6.
  • the valve guide 18 is bent at a substantially right angle on the ceiling 21 side by press molding.
  • a through hole 18 a is formed in the ceiling portion 21.
  • a flange 41 b is further formed below the valve shaft 41.
  • valve shaft 41 is inserted into the through hole 18a of the valve guide 18 so as to be rotatable with respect to the valve guide 18 and displaceable in the radial direction. It arrange
  • valve shaft 41 is inserted through the through hole 18 a and is arranged so that the upper surface of the flange portion 41 b faces the ceiling portion 21 of the valve guide 18.
  • the flange 41b is larger in diameter than the through hole 18a of the valve guide 18 so that the valve shaft 41 is prevented from coming off.
  • valve shaft 41 and the valve guide 18 are movable in the radial direction with respect to each other, the valve guide 18 and the valve guide 18 and the valve shaft 41 are not required to have a high degree of concentric mounting accuracy with respect to the arrangement positions of the valve shaft holder 6 and the valve shaft 41. Concentricity with the valve body 17 is obtained.
  • a washer (not shown) having a through-hole formed in the central part is installed.
  • the washer is preferably a metal washer having a highly slippery surface, a highly slippery resin washer such as a fluororesin, or a metal washer having a highly slippery resin coating.
  • valve guide 18 Furthermore, a compressed valve spring 27 and a spring receiver 35 are accommodated in the valve guide 18.
  • the valve body 17 is made of stainless steel, brass, or the like, and has a cylindrical rod-shaped needle portion 17n, a first taper 17a, a second taper 17b, and a third taper 17c.
  • the central axis of the valve element 17 is arranged so as to overlap the central axis L of the motor-operated valve 2.
  • FIG. 2 is an enlarged cross-sectional view of a main part that affects the flow rate characteristics of the motor-operated valve 2.
  • the valve seat member 30A is formed with a valve seat top surface 30A1, a receding region 99, a valve port 16, an inclined surface 30A2, an edge portion 19a, an upper edge portion 16a, and a lower edge portion 16b. .
  • the valve seat top surface 30A1 is a flat surface that directly contacts the valve chamber 11 on the upper side (rotor 4 side) of the valve seat member 30A.
  • the retreat area 99 is a portion located between the valve seat top surface 30A1 and the valve port 16 and retreated from the valve body 17 side.
  • a chamfer 19 that is an inclined surface extending upward is formed in the receding region 99.
  • the valve port 16 is a part that directly affects the flow rate determination, as will be described later.
  • the inner peripheral surface of the valve port 16 is arranged so as to be parallel to the central axis L of the motor-operated valve 2.
  • the inclined surface 30A2 is located below the valve port 16, and is formed so that the inner diameter of the valve seat member 30A increases downward.
  • the edge portion 19 a is a portion that forms the upper edge of the chamfer 19, and constitutes a boundary between the valve seat top surface 30 A 1 and the chamfer 19.
  • the first taper 17a is seated on the valve seat member 30A with the edge portion 19a as a seating portion.
  • the upper edge portion 16 a is an upper edge portion of the valve port 16 and also serves as a lower edge portion of the chamfer 19, and constitutes a boundary between the chamfer 19 and the valve port 16.
  • the lower edge part 16b is a part which comprises the lower edge of the valve port 16, and comprises the boundary of the valve port 16 and inclined surface 30A2. That is, the valve port 16 is formed between the upper edge portion 16a and the lower edge portion 16b.
  • the taper angle ⁇ 2 of the first taper 17a in the valve body 17 is the inclination angle ⁇ 1 of the chamfer 19 (the inclination of the surface of the chamfer 19 with respect to the central axis L of the motor-operated valve 2). ( ⁇ 1 ⁇ 2). Therefore, a space 87 having a width wider than the width of the clearance 66 described later is formed between the first taper 17a and the chamfer 19 in a state where the first taper 17a is in contact with the edge portion 19a.
  • the corner R59 is a portion in which variations in processing are particularly likely to occur in size, shape, and the like.
  • the second taper 17 b can be seated on the valve seat member 30 ⁇ / b> A to prevent the valve body 17 from biting into the valve port 16.
  • the inclination angle ⁇ 1 is preferably an angle of 10 ° to 75 °
  • the taper angle ⁇ 2 is preferably an angle of 12.5 ° to 77.5 °.
  • the corner R59 is located within a range in which the chamfer 19 is formed in the axial direction in the valve closed state. Specifically, it is formed at a position that falls within the range of the height H1 of the chamfer 19 in FIG.
  • the taper angle of the second taper 17b is much smaller than the taper angle of the first taper 17a, and the outer diameter of the second taper 17b is formed to be slightly smaller downward.
  • the taper angle of the second taper 17 b is preferably an angle of 1.5 ° or more and 10 ° or less with respect to the central axis L of the motor-operated valve 2.
  • the third taper 17c is further formed below the second taper 17b.
  • main flow rate control is performed in the second taper 17b and the third taper 17c formed below the first taper 17a seated on the valve seat member 30A.
  • the height H2 of the second taper 17b is formed to be higher than the height H1 of the chamfer 19 (H1 ⁇ H2). For this reason, in the motor operated valve 2 according to the present embodiment, the flow rate can be controlled in a wide area corresponding to the height H2 of the second taper 17b.
  • the taper angle of the third taper 17c is much smaller than the taper angle ⁇ 2 of the first taper 17a, but is larger than the taper angle of the second taper 17b.
  • the outer diameter of the third taper 17c is tapered so as to decrease downward.
  • FIG. 3 is a graph showing the relationship between the flow rate change and the pulse application amount.
  • the horizontal axis of the graph represents the amount of pulses applied to the stepping motor to move the valve body 17, and the vertical axis of the graph represents the flow rate.
  • the origin of the graph represents the valve closed state at the time of 0 pulse.
  • a broken line C in the figure represents a change in flow rate when the valve element 17 is used.
  • a broken line B representing a change in the flow rate when the valve body 114 ′ without the second taper 17b is used is shown, as shown in FIG. .
  • the clearance 66 between the second taper 17b and the valve port 16 becomes narrower than the gap between the first taper 17a and the edge portion 19a, and the clearance 66 is formed between the valve body 17 and the valve port. 16 is the minimum width of the gap generated between the two. For this reason, the flow rate region 62 in the low opening range until the second taper 17 b passes through the valve port 16 is determined by the width of the clearance 66.
  • the degree of increase is suppressed, and the second taper 17b rises and gradually increases as the clearance 66 increases.
  • the width of the clearance 66 is preferably 1 ⁇ m or more and 30 ⁇ m or less.
  • the function of the first taper 17a is limited to the seating function as much as possible, and mainly by controlling the flow rate with the second taper 17b, The flow rate can be accurately controlled. Further, by forming the taper angle ⁇ 2 of the first taper 17a to be larger than the inclination angle ⁇ 1 of the chamfer 19 ( ⁇ 1 ⁇ 2), the boundary between the first taper 17a and the second taper 17b is the valve port 16. Therefore, it is possible to prevent the flow characteristics at the time of rising from being different for each motor-operated valve 2 due to the variation in processing for each valve element 17.
  • the upper edge 16a of the valve port 16 is always close to the second taper 17b or the third taper 17c when the valve body 17 is raised or lowered, so that the flow rate control in the flow rate region 62 shown in FIG. Is performed by the upper edge 16a.
  • the clearance 66 between the upper edge portion 16a of the valve port 16 and the second taper 17b or the third taper 17c gradually increases and the flow rate increases.
  • the receding region 99 may be a notch.
  • a notch 79 having an L-shaped cross section may be formed above the valve port 16.
  • the notch 79 is formed with an edge 79a, a wall 79c, a floor 79d, and an upper edge 16a. Due to this notch 79, the upper side of the valve seat member 30A is notched annularly.
  • the edge portion 79a is a portion that forms the upper edge of the wall portion 79c, and constitutes the boundary between the valve seat top surface 30A1 and the notch 79.
  • the first taper 17a is seated with the edge 79a of the notch 79 as a seat.
  • variety of the clearance 66 between the 1st taper 17a and the notch 79 is provided.
  • a space 87 is formed.
  • the wall portion 79 c is a side wall that defines the outer periphery of the notch 79, and is disposed so as to be parallel to the central axis L of the motor-operated valve 2.
  • the floor portion 79 d is a portion that defines the bottom surface of the notch 79, and is orthogonal to the central axis L of the motor-operated valve 2.
  • the wall portion 79c does not have to be strictly parallel to the central axis L, and may be slightly inclined.
  • the floor portion 79d does not need to be strictly orthogonal to the central axis L and may be slightly inclined.
  • the upper edge portion 16 a is a portion forming the upper edge of the valve port 16 and a portion forming the edge portion of the floor portion 79 d on the valve body 17 side, and constitutes a boundary between the notch 79 and the valve port 16.
  • the second taper 17b can accurately control a minute flow rate in the low opening range. Further, by forming the second taper 17b so that the height H2 of the second taper 17b is higher than the height H3 of the notch 79 (H3 ⁇ H2), the flow rate is controlled in a wide area corresponding to the height H2 of the second taper 17b. It can be performed.
  • a constriction 89 may be provided between the first taper 17a and the second taper 17b.
  • the boundary portion between the first taper 17a and the second taper 17b is recessed from the surface of the valve body 17, when the first taper 17a is seated on the valve seat member 30A, the first taper 17a and the valve A space 87 wider than the clearance 66 is formed between the ports 16. Also by this, it can avoid that the boundary part of the 1st taper 17a and the 2nd taper 17b sits on the valve port 16, and it can prevent the flow volume characteristic at the time of start-up varying for every motor-operated valve 2.
  • the second taper 17b can accurately control a minute flow rate in the low opening range.
  • the second taper 17b has an extremely small taper angle that is substantially parallel to the central axis L has been described as an example.
  • FIG. 17b may have a predetermined taper angle ⁇ .
  • the main flow rate control is performed by the upper edge portion 16a. Is done by.
  • the clearance 66 between the upper edge part 16a of the valve port 16 and the 2nd taper 17b or the 3rd taper 17c becomes large gradually, and flow volume increases.
  • the taper angle ⁇ shown in FIG. 6 is preferably an angle between 1 ° and 30 °.
  • valve body 17 includes the third taper 17c
  • the valve body 17 does not necessarily include the third taper 17c.
  • the valve body 17 may include a further taper in addition to the first taper 17a, the second taper 17b, and the third taper 17c.
  • the motor operated valve 2 of the present embodiment is used as an electronic expansion valve provided between a condenser and an evaporator of a refrigeration cycle system, for example.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Lift Valve (AREA)
PCT/JP2017/035189 2016-09-30 2017-09-28 電動弁 Ceased WO2018062376A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CN202110754553.6A CN113418014B (zh) 2016-09-30 2017-09-28 电动阀
JP2018542848A JP6904968B2 (ja) 2016-09-30 2017-09-28 電動弁
CN202110756179.3A CN113324054B (zh) 2016-09-30 2017-09-28 电动阀
CN201780055963.3A CN109715997B (zh) 2016-09-30 2017-09-28 电动阀

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-193725 2016-09-30
JP2016193725 2016-09-30

Publications (1)

Publication Number Publication Date
WO2018062376A1 true WO2018062376A1 (ja) 2018-04-05

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PCT/JP2017/035189 Ceased WO2018062376A1 (ja) 2016-09-30 2017-09-28 電動弁

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JP (3) JP6904968B2 (https=)
CN (3) CN113324054B (https=)
WO (1) WO2018062376A1 (https=)

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CN113932022A (zh) * 2018-07-06 2022-01-14 株式会社鹭宫制作所 电动阀以及冷冻循环系统
JP2022033227A (ja) * 2020-08-26 2022-02-28 株式会社不二工機 電動弁
US20220136608A1 (en) * 2020-10-30 2022-05-05 Illinois Tool Works Inc. Valve device for shutting off or controlling a flow of a fluid
CN114857288A (zh) * 2018-08-31 2022-08-05 株式会社鹭宫制作所 电动阀以及冷冻循环系统
KR20230066469A (ko) * 2020-10-12 2023-05-15 제지앙 둔안 아트피셜 인바이런먼트 컴퍼니 리미티드 유량 조절 밸브

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JP7409982B2 (ja) * 2020-07-02 2024-01-09 株式会社鷺宮製作所 電動弁及び冷凍サイクルシステム
CN112032311B (zh) * 2020-07-27 2022-04-12 北京精密机电控制设备研究所 一种多级精密配合的轴向步进机构的装配方法
CN114352728A (zh) * 2020-10-12 2022-04-15 浙江盾安人工环境股份有限公司 流量调节阀
CN115467979B (zh) * 2021-06-11 2025-09-19 浙江盾安禾田金属有限公司 流量调节阀
DE102024116917A1 (de) * 2024-06-17 2025-12-18 Minebea Mitsumi Inc. Ventil, insbesondere expansionsventil oder abschaltventil

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