EP0479020B1 - Dampfumformventil mit Spindelantrieb - Google Patents

Dampfumformventil mit Spindelantrieb Download PDF

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Publication number
EP0479020B1
EP0479020B1 EP19910115657 EP91115657A EP0479020B1 EP 0479020 B1 EP0479020 B1 EP 0479020B1 EP 19910115657 EP19910115657 EP 19910115657 EP 91115657 A EP91115657 A EP 91115657A EP 0479020 B1 EP0479020 B1 EP 0479020B1
Authority
EP
European Patent Office
Prior art keywords
spindle
auxiliary
steam
main
throttle body
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.)
Expired - Lifetime
Application number
EP19910115657
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0479020A1 (de
Inventor
Hermann Dörr
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Publication of EP0479020A1 publication Critical patent/EP0479020A1/de
Application granted granted Critical
Publication of EP0479020B1 publication Critical patent/EP0479020B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G5/00—Controlling superheat temperature
    • F22G5/12—Controlling superheat temperature by attemperating the superheated steam, e.g. by injected water sprays
    • F22G5/123—Water injection apparatus
    • F22G5/126—Water injection apparatus in combination with steam-pressure reducing 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8158—With indicator, register, recorder, alarm or inspection means
    • Y10T137/8225—Position or extent of motion indicator
    • Y10T137/8275—Indicator element rigidly carried by the movable element whose position is indicated
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86928—Sequentially progressive opening or closing of plural valves
    • Y10T137/86936—Pressure equalizing or auxiliary shunt flow
    • Y10T137/86944—One valve seats against other valve [e.g., concentric valves]
    • Y10T137/86984—Actuator moves both 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87571—Multiple inlet with single outlet
    • Y10T137/87652—With means to promote mixing or combining of plural fluids
    • Y10T137/8766—With selectively operated flow control means
    • Y10T137/87668—Single actuator operates plural flow control means

Definitions

  • the invention relates to a steam conversion valve with a spindle drive, with a first valve with a first throttle body for controlling a first steam flow, wherein the thrust forces of a spindle drive can be transmitted from an associated spindle to the throttle body to open and close the first valve, and with a second Valve with a second throttle body for controlling a second steam flow, means for mixing an atomizing steam flow with a cooling water flow being provided.
  • a steam conversion valve according to the preamble of claim 1 is known from DE-B-1 071 094 (D1) or from DE-C-712 163 (D2).
  • D1 a double seat steam conversion valve is described, in which both a pre-stroke valve and the closure piece of a second valve each control a part, for example 40% and 60%, of the main steam flow, within two, one of the two valves assigned throttle zones, the steam flow is enveloped by a rotating water ring and is to mix with it.
  • annular chambers are assigned to each of the two valve throttling points, into which the cooling water is introduced tangentially. If such annular chambers high closing forces of the valve lifter exposed to the risk of breakage. In addition, it is difficult to achieve an equally good atomization of the water droplets with two throttle points working in parallel.
  • (D2) is also a double-seat valve with closure pieces arranged on the valve tappet at a fixed distance from one another.
  • the valve seat of one closure piece is used to inject the cooling water via a corresponding nozzle ring, the passage cross section of the other closure piece is provided for passage of a partial steam flow without water injection, although this second valve seat can also be provided with means for water injection.
  • the rigid spacing of the valve seats and valve lifters gives rise to the problem of the exact coordination of the two valves with one another; if one valve seat and one closure piece are reground, this must also be done with the other valve, in such a way that the intended control behavior is retained.
  • This known valve according to (D2) has no lift valve, so that considerable pressure forces act on the valve when opening and closing.
  • DE-A-1 959 446 discloses a steam conversion valve with a main valve for controlling the main steam flow and an auxiliary valve, the main and auxiliary spindles being connected to one another via a spring-elastic coupling. This allows a staggered closing or opening of the two valves , the auxiliary valve is only used to control a cooling water flow and not the atomizing steam flow. Furthermore, in this known valve, first the auxiliary valve and then the main valve is closed (when opening the first main valve and then the auxiliary valve), so that a pressure-relieving effect is not achieved during the closing or opening process.
  • the invention is intended to create a steam conversion valve with a spindle drive, by means of which the difficulties described can be overcome, namely by precisely controlling a main throttle body for the main steam flow by means of a main spindle and an auxiliary throttle body for the atomizing steam flow by means of an auxiliary spindle.
  • Another object is to create the structural requirements for the steam converter valve to be actuated in a compact design with both a rotary drive and a linear actuator, without having to make any fundamental changes to the valve housing, the throttle bodies and the spindles.
  • the main spindle In the closed direction, the main spindle is first moved to the end position, and only then is the auxiliary spindle actuated to interrupt the atomizing steam flow. In or below the main throttle body, the atomized cooling water experiences a 180 ° deflection and is thus optimally distributed into the main steam flow without directly reaching the valve or pipe walls.
  • a fixed cooling water inlet pipe is arranged in the low-pressure chamber of the outflow side of the steam conversion valve, into which the main throttle body is immersed with a nozzle pipe serving to introduce the atomizing steam flow.
  • the steam inlet of an axial nozzle pipe channel forms the valve seat for the auxiliary throttle body, atomizing steam supply channels leading to this steam inlet, which are open on the inlet side to the steam inflow side of the valve.
  • the auxiliary valve seat defines the passage cross section for a connection between the outlet ends of the atomizer vapor supply channels and the nozzle tube channel, so that the connection of the atomizer vapor supply channels is also closed or opened when the auxiliary valve is closed / opened.
  • the nozzle tube is provided at its end entering the cooling water inlet tube with a cone body which serves for the flow conduit of the incoming cooling water to the inlet tube wall.
  • Swirl vanes for generating a cooling water swirl flow are arranged on an annular channel downstream of the cone body on the outflow side of the cooling water. In this way, the cooling water is swirled before atomization in order to obtain the most symmetrical water introduction possible even when the steam converter valve is in the horizontal position.
  • a concentric, compact design is achieved by a preferred embodiment according to claim 6, according to which the pipe socket of the nozzle pipe forms the coaxial extension of a central channel of the main spindle, in which the auxiliary throttle body of the auxiliary spindle, which is designed as a tappet, is mounted in a longitudinally displaceable and sealing manner, in the transition region of the central Channel to the nozzle tube channel of the auxiliary valve seat, which in particular has conical seat surfaces, is arranged for the auxiliary throttle body.
  • the main throttle body or the nozzle tube are provided with axially and circumferentially distributed inlet channels for the main steam (orifice throttle body) or nozzle bores for the atomizer steam.
  • the special design of the first and second resilient couplings and a linear actuator or a rotary actuator are treated as the two valve spindles, the main and the auxiliary spindle, common spindle drive.
  • FIG. 1 shows the basic structure of a steam conversion valve according to the invention.
  • the steam forming process uses double-spindle-controlled steam pressure reduction and steam-atomized cooling water.
  • the steam conversion valve VU1 consists of a main valve V1, which is combined with an auxiliary valve V2.
  • the main spindle 5 with the main throttle body 6 is actuated via the split spindle nut arrangement 2, which is constructed to be non-rotatable by spring wedges 21, 22 and consists of the first spindle nut 2a and the second spindle nut 2b.
  • the sealing surface 6a of the main throttle body 6 is pressed onto the valve seat 7, ie corresponding seating surfaces 7a.
  • a prestressed compression spring arrangement 3 is inserted between the first (upper) spindle nut 2a and the second (lower) spindle nut 2b, which in a preferred embodiment is designed as a plate spring or plate spring assembly. To simplify matters, a (first) disk spring 3 is therefore discussed below.
  • the upper part 9 of the auxiliary spindle 50 is screwed directly into the first spindle nut 2a.
  • the thread pitch of the auxiliary spindle upper part 9 in the first spindle nut 2a corresponds exactly to the thread pitch of the main spindle 5 in the second spindle nut 2b.
  • the first and second spindle nuts 2a, 2b and the preloaded disk spring 3 inserted between them form the first spring-elastic coupling FK1.
  • the second resilient coupling FK2 is inserted in the form of a coupling piece with the prestressed disk spring assembly 11, the coupling piece connecting the two auxiliary spindle parts 9, 10 to one another in a rotationally secure manner.
  • the preloaded plate spring assembly 11 is referred to in the following for simplicity as the second plate spring, although in principle this could also be a preloaded compression spring or helical compression spring arrangement.
  • the stroke position indicator and anti-rotation device 12 are located on the main spindle 5.
  • the auxiliary spindle 50 is equipped with the anti-rotation device 4 relative to the main spindle 5, which, if required, for example for control purposes, can also serve as a stroke position indicator.
  • the auxiliary valve designated as a whole by V2 is arranged and mounted coaxially and centrally with the main spindle 5 with its auxiliary spindle 50 and its auxiliary throttle body 10a, which forms part of the lower spindle part 10; the outlet of its auxiliary seat 16, which is located within the main throttle body 6, opens into the nozzle tube 17, which projects into the cooling water inlet tube 14.
  • the inlet side of the auxiliary seat 16 is connected to the high-pressure chamber 13 of the steam conversion valve VU1 via the atomizer steam supply channels 19, designed as radial bores.
  • the high-pressure chamber 13 is on the inflow side 13 'of the valve VU1.
  • the presetting of the auxiliary spindle 50 is carried out in such a way that when the first disc spring 3 is stretched (ie the position of the main spindle 5 is greater than 0%) with the anti-rotation device 4 released and by turning the auxiliary spindle 50 with its upper and lower part 9, 10 a maximum stroke (distance between Auxiliary seat 16 and auxiliary spindle 50) of the auxiliary spindle 50 is set, which corresponds approximately to half the spring deflection of the first plate spring 3.
  • valve VU 1 in the closing direction is explained below.
  • the auxiliary spindle 50 has assumed the preset maximum stroke, ie the inflow side 13 'is connected via the feed channels 19 and the nozzle tube 17 to the outflow side 18' (low pressure chamber 18).
  • the atomizer vapor can flow from the inflow side 13 'through the supply channels 19, the (open) auxiliary seat 16 and the free nozzle bores 17c of the nozzle tube 17 - with atomization of the cooling water flowing in through the cooling water inlet tube 14 - into the low pressure chamber 18.
  • the main steam flow flows from the inflow side 13 'into the low-pressure chamber 18.
  • the main steam flow f11 is mixed intensively with the atomized cooling water, which is caused by a mixture of the atomizing steam flow f12 the cooling water flow f2 has arisen, so that the resulting formed steam flow f11 + f12 + f2 results (cf. the corresponding flow arrows).
  • the total amount of the incoming steam is designated f1, which is divided into the main steam flow f11 and the atomizing steam flow f12.
  • the starting position is assumed to be the tightly closed state of the valve.
  • the expansion of the plate springs 3 and 11 begins.
  • the auxiliary spindle lower part 10 begins to lift off the auxiliary seat 16 and continuously opens the connection from the inflow side 13 via the nozzle tube 17 to the outflow side 18 ', whereby the atomizing vapor stream f12 is brought to the - depending on the pressure gradient - maximum intensity.
  • the full amount of atomizing steam is already available for the cooling water f2 flowing in via the cooling water inlet pipe 14, which is set in swirl via the swirl vanes (deflection fins) 15 attached to the nozzle pipe 17. Only when the disc spring 3 is fully extended does the opening movement of the main spindle 5 with the main throttle body 6 and thus the flow of the main steam flow f11 begin.
  • the steam conversion valve VU1 according to FIG. 1 (and accordingly also that VU2 according to FIG. 2) has a spindle drive for a main valve V1 and for an auxiliary valve V2.
  • the main valve V1 of the steam conversion valve VU1 has a main throttle body 6 for controlling the main steam flow f11, the thrust forces of a spindle drive 1 (a rotary drive in FIG. 1) being able to be transmitted from an associated main spindle 5 to the main throttle body 6 in order to open and close the main valve V1.
  • the steam conversion valve VU1 also includes the auxiliary valve V2, which has an auxiliary throttle body 10a for controlling an atomizing steam flow f12, the thrust forces of the spindle drive 1 being able to be transmitted from an associated auxiliary spindle 50 to the auxiliary throttle body 10a in order to open and close the auxiliary valve V2.
  • the actuating forces of the common spindle drive 1 for the main and auxiliary spindles 5, 50 can each be transmitted to the main throttle body 6 and the auxiliary throttle body 10a via first and second spring-elastic couplings 3 and 11, the two spindles 5, 50 being matched to one another such that the main throttle body 6 closes during the closing operation before the auxiliary throttle body 10a reaches its auxiliary valve seat 16, so that the main steam flow f11 is shut off from the atomizer steam flow f12.
  • the tuning is such that during the opening process, the auxiliary throttle body 10a opens its auxiliary valve V2 before the main throttle body 6 leaves its main valve seat 7, so that the atomizer vapor stream f12 forms before the main vapor stream f11.
  • the structural details explained below are particularly advantageous for realizing the prescribed mode of operation.
  • the in the low pressure chamber 18 of the outflow side 18 'arranged cooling water inlet pipe 14 is fixed, the amount of cooling water can be adjusted to desired values by a cooling water setting valve, not shown.
  • the main throttle body 6 is immersed in the cooling water inlet pipe 14 with its nozzle pipe 17 serving to introduce the atomizing steam flow f12.
  • the steam inlet 17b of an axial nozzle tube duct 17a forms the valve seat (auxiliary seat) 16 for the auxiliary throttle body 10a.
  • the atomizer steam supply channels 19 lead to this steam inlet 17b and are open on the inlet side to the inflow side 13 (high-pressure chamber) of the valve VU1.
  • the auxiliary valve seat 16 defines the passage cross section for a connection between the outlet ends of the atomizer vapor supply channels 19 and the nozzle tube channel 17a, so that the connection of the supply channels 19 is also closed or opened when the auxiliary valve V2 is closed / opened.
  • the main throttle body 6, which has essentially a hollow cylindrical shape, has a cylindrical outer wall 6b on its outer circumference, which extends from its seat surfaces 6a in the direction of the low-pressure chamber 18.
  • the axes of the inlet channels 20 run radially to the valve axis y'-y 'in the example shown.
  • the nozzle tube 17 is provided at its end immersed in the cooling water inlet tube 14 with a cone body 23 which serves for the flow conduit of the incoming cooling water f2 to the inlet tube wall 14a.
  • Swirl blades 15 (which could also be referred to as deflection fins) for generating a cooling water swirl flow are arranged in a ring channel 24 connected to the cone body 23 on the outflow side of the cooling water.
  • the nozzle tube 17 is, as can be seen, designed as a centrally located and axially projecting pipe socket on the outflow side 18 'of the main throttle body 6.
  • this pipe socket of the nozzle pipe 17 is the coaxial extension of a central channel 5a of the main spindle 5, in which the auxiliary throttle body 10a of the auxiliary spindle 50, which is designed as a tappet, is mounted in a longitudinally displaceable and sealing manner.
  • the auxiliary valve seat 16, which in particular has conical seat surfaces, for the auxiliary throttle body 10a is arranged in the transition region from the central channel 5a to the axial nozzle tube channel 17a.
  • the nozzle tube 17 is provided with a plurality of axially and circumferentially distributed nozzle bores 17c for injecting the atomizer vapor stream f12 into the cooling water stream f2. In the open position of the main throttle body 6, all of these nozzle bores 17c are free, i.e. no longer dip into the inlet pipe 14.
  • the main throttle body 6 has on its inside facing the outflow side 18 'of the steam an annular deflection chamber 25, which is penetrated centrally by the nozzle tube 17 and is shaped by curved profiled wall walls. and bottom portions 6c of the main throttle body 6 is limited.
  • the inner circumference of the jacket wall portion initially runs obliquely inward at an acute angle to the valve axis y′-y ′ and then merges into a curved region near the ground, which in turn merges into the outer circumference of the nozzle tube 17 with a spiraling curvature .
  • the length adjustment device of the auxiliary spindle 50 is formed by the latter even when the anti-rotation lock 4 is released by screwing it more or less far into the threaded bore 26 of the first spindle nut 2.
  • the common drive member for the main and auxiliary spindle 5, 50 is formed by the shaft journal 27 of the rotary drive 1. Following the central channel 5a within a shaft part 5b of the main spindle 5, an enlarged cavity 5c is provided, and within this cavity 5c the auxiliary spindle 50 with its second spring-elastic coupling FK2 can be moved in the stroke direction ⁇ y.
  • the second spring-elastic coupling FK2 is preferably a spring cage with the prestressed disc spring 11, the spring cage 28 being seated on the auxiliary spindle lower part 10 and the auxiliary spindle upper part 9 having a reinforced head part 9a being longitudinally displaceable and loaded by the disc spring 11 and being loaded by a basket cover 28a is caught.
  • a spring key to prevent rotation between the upper spindle part 9 and the spring cage 28 is indicated.
  • this or its shaft part 5b is guided with laterally projecting roller arms 12 in longitudinal slots 30a of the peripheral wall of a valve lantern 30 in the stroke direction ⁇ y, the guide rollers being denoted by 12a.
  • the roller arms 4 with guide rollers 4a of the spring cage 28, the guide slots being designated 5d here.
  • the first spindle nut 2a is rotatably mounted by means of a first pressure bearing 31, which is supported in the housing cover 32, the second spindle nut 2b is correspondingly rotatably supported by means of a second pressure bearing 33, which is supported on an internal ring flange 30b of the valve lantern 30.
  • the first spindle nut 2a is connected in a rotationally fixed manner to the spindle drive 1 via the shaft journal 27 with the spring wedge 21; it forms with its internal thread 26 a screw bearing for the rotationally secured auxiliary spindle 50 for its axial movement.
  • the second spindle nut 2b is mounted on a guide shaft 2a1 of the first spindle nut 2a in a rotationally fixed but axially displaceable manner.
  • the first spring-elastic coupling FK1 is inserted in an axial intermediate space 34 between the first (2a) and the second spindle nut 2b.
  • the second spindle nut 2b forms, with a threaded shaft 2b1, a screw bearing for the main spindle 5, which is secured against rotation, for its axial movement.
  • the shaft part 5b of the main spindle 5 is slidably sealed by a stuffing box 35, the sealing packing is designated 35a, the end cap 35b. Accordingly, the auxiliary spindle 50 is guided in a sealing manner to the outside by means of the stuffing box 36 and thus this lead-through point is also sealed to the outside.
  • the stuffing box cover is labeled 36b, the pack 36a.
  • the stuffing box 35 sits on the inner circumference of an intermediate piece 37 between the valve housing 38 and the valve lantern 30. This intermediate piece 37 serves for the sealing flange connection between the valve lantern 30 and the valve housing 38 and forms a precise guide point for the main spindle 5.
  • the rotary drive 1 can in principle be an electrical, hydraulic or pneumatic rotary drive; it is preferably an electric control motor that has one of its setpoint / actual value difference gets the appropriate manipulated variable from the control system.
  • the steam conversion valve VU2 shown in FIG. 2 is constructed on the steam and water side in the same way as that according to FIG. 1, which is why the same parts are also provided with the same reference numerals.
  • a hydraulic linear actuator 1 'with a hydraulic piston-cylinder system 39 is provided here.
  • the cylinder structurally combined with the valve housing cover 32 is designated 39a, the piston 39b and the piston rod 39c.
  • the piston rod 39c is coupled via a clutch 40 to the drive rod 41 common to the two valve spindles, the main spindle 5 and the auxiliary spindle 50.
  • the latter is connected via the first spring-elastic coupling FK1 to the main spindle 5 and via a length adjustment device 42 to the auxiliary spindle upper part 9, the latter being coupled to the auxiliary spindle lower part 10 via the second spring-elastic coupling FK2.
  • the first spring-elastic coupling FK1 has a spring cage with the housing 43, the housing cover 43a, the housing base 43b and the prestressed disk spring assembly 3 arranged in the interior of the housing 43.
  • the flange 41a of the drive rod 41 is caught within the housing 43 by the attached and fastened housing cover 43a.
  • the design of the second resilient coupling FK2 in FIG. 2 is - except for the anti-rotation lock that is not required here - as in the first example according to FIG.
  • the adjustment of the auxiliary spindle 50 in relation to the main spindle 5 takes place in such a way that the first one is not pressed in Spring-elastic coupling FK1 (position of main spindle 5 greater than 0%) is adjusted via the adjusting device 42 a maximum stroke (distance between auxiliary seat 16 and auxiliary spindle 50) of the auxiliary spindle 50, which corresponds approximately to half the spring deflection of the first spring-elastic coupling FK1.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lift Valve (AREA)
EP19910115657 1990-09-29 1991-09-16 Dampfumformventil mit Spindelantrieb Expired - Lifetime EP0479020B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE4030902 1990-09-29
DE4030902 1990-09-29
DE4040736 1990-12-19
DE4040736 1990-12-19

Publications (2)

Publication Number Publication Date
EP0479020A1 EP0479020A1 (de) 1992-04-08
EP0479020B1 true EP0479020B1 (de) 1994-11-23

Family

ID=25897328

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19910115657 Expired - Lifetime EP0479020B1 (de) 1990-09-29 1991-09-16 Dampfumformventil mit Spindelantrieb

Country Status (4)

Country Link
US (1) US5113903A (ja)
EP (1) EP0479020B1 (ja)
JP (1) JPH04262175A (ja)
DE (1) DE59103579D1 (ja)

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DE4304972C2 (de) * 1993-02-18 1996-12-05 Holter Gmbh & Co Dampfumformventil
DE19719120C2 (de) * 1997-05-07 2000-10-12 Schneider Bochumer Maschf A Vorrichtung zur Kühlung von Heißdampf
CN106090419A (zh) * 2016-08-23 2016-11-09 成都欧浦特控制阀门有限公司 一种防冲蚀的阀门密封结构
CN106286853A (zh) * 2016-08-23 2017-01-04 成都欧浦特控制阀门有限公司 使用寿命长的控制阀
CN108061187B (zh) * 2017-12-18 2019-09-24 马奔 一种自动化专业用可调式阀门
CN108087570B (zh) * 2017-12-18 2020-04-07 马奔 一种自动化专业用可调式阀门的使用方法
JP6909740B2 (ja) * 2018-01-31 2021-07-28 株式会社鷺宮製作所 電動弁及び冷凍サイクルシステム
RU193754U1 (ru) * 2019-01-10 2019-11-13 Акционерное общество "Опытное Конструкторское Бюро Машиностроения имени И.И. Африкантова" (АО "ОКБМ Африкантов") Комбинированный привод двухзапорного клапана
JP7361628B2 (ja) * 2020-02-19 2023-10-16 株式会社鷺宮製作所 電動弁及び冷凍サイクルシステム
JP7449844B2 (ja) * 2020-11-27 2024-03-14 株式会社鷺宮製作所 電動弁
RU2764950C1 (ru) * 2021-05-24 2022-01-24 Александр Михайлович Юрасов Двухзапорный клапан

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Publication number Publication date
JPH04262175A (ja) 1992-09-17
US5113903A (en) 1992-05-19
DE59103579D1 (de) 1995-01-05
EP0479020A1 (de) 1992-04-08

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