WO2004076896A1 - Ensemble de soupape de retenue a bille - Google Patents

Ensemble de soupape de retenue a bille Download PDF

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Publication number
WO2004076896A1
WO2004076896A1 PCT/HU2004/000013 HU2004000013W WO2004076896A1 WO 2004076896 A1 WO2004076896 A1 WO 2004076896A1 HU 2004000013 W HU2004000013 W HU 2004000013W WO 2004076896 A1 WO2004076896 A1 WO 2004076896A1
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WO
WIPO (PCT)
Prior art keywords
valve
core
valve stem
valve assembly
ball valve
Prior art date
Application number
PCT/HU2004/000013
Other languages
English (en)
Inventor
Ferenc BÉDA
Original Assignee
Beda Ferenc
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 Beda Ferenc filed Critical Beda Ferenc
Publication of WO2004076896A1 publication Critical patent/WO2004076896A1/fr

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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
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/08—Details
    • F16K5/14—Special arrangements for separating the sealing faces or for pressing them together
    • F16K5/20—Special arrangements for separating the sealing faces or for pressing them together for plugs with spherical surfaces
    • F16K5/204—Special arrangements for separating the sealing faces or for pressing them together for plugs with spherical surfaces with the plugs or parts of the plugs mechanically pressing the seals against the housing

Definitions

  • the present invention relates to an improved ball valve assembly suitable for use in supply systems as well and calibrating systems, especially in the oil and gas industry, and also in fields of application where the fluids to be dealt with are heavily contaminated and/or corrosive substances.
  • the improved ball valve assembly of the invention provides, in the valve's closed status of operation and independently from the prevailing fluid pressure, for a simultaneous and positive tight sealing in both directions of flow.
  • the improved ball valve assembly comprises a valve core of substantially spheroid shape. The valve core is located for operation within a valve housing having built-in valve seats and a bonnet including a packing gland.
  • the valve core has a thoroughfare flow port and sealing surfaces capable of estabHs ing and mamtaining, in co-operation with the built-in valve seats in the housing, a tight seal against the built-in valve seats of the housing.
  • the valve core is provided with a coupling aperture and, in a position diametrically opposite to the latter, with a substantially cylindrical radial protrusion serving as a mount stud for the valve core within the housing.
  • the improved ball valve assembly of the invention further comprises a valve stem arranged diametrically opposite to and in axial alignment with the substantially cylindrical mount stud of the core.
  • the valve stem has a first stem end portion facing the valve core, and a second stem end portion which is coupled to a drive means capable of moving, either manually or by means of a remote controlled power actuated device, the valve stem within the bonnet in both axial directions towards and away from the core.
  • the valve stem is associated with a mechanism for turning the same at angles of substantially 90° in one or the other sense of rotation when it is caused by the drive means to travel in the one or the other axial direction.
  • Ball valves are known shutoff armatures widely and increasingly used and applied in industry, including the crude oil and natural gas industry, because in contrast to other types of shutoff armatures such as e.g. gate or plug valves, ball valves can be operated at a comparatively lower torque of actuation and at the same time, they have a maximum free cross section of flow in their open status of operation.
  • valve refers to an ideal shape of the shutoff member, as often called the "core” of the valve.
  • core of the valve.
  • valve cores having the shape of a "body of rotation” exhibiting, in combination with flattened and/or recessed areas serving other functions, spherical surface areas which provide for the desired sealing effect.
  • ball valves are either designed as shutoff armatures having a core mounted for rotation in the valve housing, or as ball valves having a floating core where the substantially ball-shaped core is allowed, within structural limits, of free displacement in the direction of the flow of fluid in the housing.
  • ball valves of the US company CAMERON using a rotating sealing system and known ball valves having seal rings made of teflon, such valves being manufactured by the French company MAPEGAZ, are worth mentioning.
  • the core is mechanically wedged tightly against the valve seat, assuring positive shut-off. Prior to turning, the core tilts away from the seat and the rotation of the core can be effected without seal rubbing.
  • the core is actuated by a valve stem coupled to a drive means capable of moving, either manually or by means of a power aided or actuated device, the valve stem in axial direction towards and away from the core.
  • One object of the present invention is to provide an improved ball valve assembly by which simultaneous tight seal and thus, zero leakage with full sepaiation of the line sections of significantly different pressure values is maintained in both flow directions.
  • Another objective of the present invention is to provide a ball valve assembly in which, also in the open thoroughfare status of the valve, space regions receiving means and functional component parts used and serving for a controlled actuation of the valve assembly only, are separated under hermetic seal from the inside region of the valve housing in which the core is mounted for rotation.
  • the improved ball valve assembly of the invention should be of a design and structure ensuring that all the advantages inherent in state-of-the-art approaches, such as low torque requirement for easy operation, possibility of using if so desired, as an alternative for or in addition to a manual drive means, remote controlled power actuated, especially hydraulic and pneumatic devices for valve operation, and the provision of a possible maximum of free cross section of flow for the fluid with a negligible pressure loss within the valve, are maintained.
  • the joint synchronised movement of the two separate core segments can be controlled and effected by having the conventional prior ait valve stem perform a double function.
  • the valve stem performs, on the one hand and as known from prior art devices of the kind concerned, a substantially 90° rotation of the valve core between its extreme positions of operation the sense of such a rotation depending on the direction of the axial movement of the stem.
  • valve stem of the ball valve assembly of the invention when caused to further longitudinal movement in the one or the other axial direction, functions as a driving means for a closed link mechanism capable, according to one of the essential novel features of the invention, of symmetrically and synchronously moving the core segments towards and away from their respective valve seats.
  • valve core consists of two separate core segments of identical shape derived by separating, preferably cutting a valve core of substantially spheroid shape into two halves along its median plane incorporating the longitudinal axis of the thoroughfare flow port.
  • the core segments are allowed within the housing of the ball valve assembly of both, synchronous co-rotation at an angle of substantially 90° in both senses of rotation around the longitudinal axis of the valve stem, and a synchronous movement relative to each other towards and away from their common median plane.
  • Parallel annular spherical zones of the core segments are designed and shaped as sealing surface areas providing a hermetic seal when, in the closed status of operation of the valve assembly, the core segments are moved towards and wedged against the built-in valve seats of the housing.
  • the ball valve assembly of the invention is further provided with a valve stem head secured rigidly to one end portion of the valve stem.
  • the valve stem head is arranged, at least partially, and allowed of longitudinal movement in both axial directions only, within the coupling aperture of the valve core.
  • the core segments are mounted on the valve stem head by means of a closed link mechanism which is capable of symmetrically and synchronously moving, in the closed status of the ball valve assembly, the core segments towards and away from the built-in valve seats, respectively, when the valve stem is caused by the drive means to its additional longitudinal movement mentioned further above, in the one or the other axial direction.
  • the closed link mechanism coupling the core segments and the valve stem head consists of guide slots of mirror symmetric arrangement as against the common median plane of the valve core, and of a pair of guide pins seated and secm-ed in respective bores of the core segments of the valve core.
  • the guide pins are passed, respectively, through the guide slots of the valve stem head, whereby said additional up and down axial movements of the valve stem head are converted, deteirnined by the actual shape of said guide- slots, into relative movements of the core segments away and towards each other and their respective valve seats.
  • the valve stem head has an upper head portion of substantially cylindrical shape, and a lower head portion of substantially rectangular cross section.
  • the shape of the lower head portion corresponds, in cross section, with that of the coupling aperture in the valve core.
  • the guide slots are of mirror symmetric arrangement as against the common median plane of the valve core, and each guide slot consists of two adjoining slot sections, namely a lower slot section substantially parallel to, and an upper slot section inclined at an angle ⁇ , in respect to and away from the common median plane of the valve core.
  • the guide pins are seated and secured in respective bores of the core segments of the valve core, the bores lying in mirror symmetrical arrangement as against the common median plane, and in distant parallel relationship to the central axis of the thoroughfare port of the valve core.
  • the upper head portion of the valve stem head is provided with a central blind bore and a transverse bore for receiving and rigidly securing, via a transverse coupling bolt, the valve stem head to the first end portion of the valve stem.
  • the upper head portion of the valve stem head further comprises a protruding annular bevel face rim around the circumference of the central blind bore.
  • a preferred mechanism for turning the valve stem at angles of substantially 90° in one or the other sense of rotation when the valve stem is caused by its drive means to axial movement in the one or the other direction, respectively consists of two opposite spiral grooves featured on the outer surface of the valve stem, and of two driving pins of fixed position relative to the housing of the ball valve assembly.
  • the driving pins co-operate, when the valve stem is moved between them in axial direction, with the spiral grooves of the valve stem.
  • Each spiral groove consists of three groove sections of which two outermost groove sections are shaped as perpendicular flat areas of substantial axial length lying parallel with the longitud nal axis of the valve stem. These outermost groove sections are interconnected by a twisted quarter turn shaped intermediate groove section.
  • valve stem is caused to a substantially 90° rotation around its longitudinal axis.
  • the valve stem is received and guided in a manner allowing both, its rotation and axial movement within a mounting socket which is, as a co-axial component part, releasably secm-ed to the bonnet of the housing of the ball valve assembly.
  • the driving pins co-operating, respectively, with the spiral grooves of the valve stem are seated and securely held in distant parallel transverse bores within the mounting socket.
  • the substantially cylindrical radial protrusion serving as a mount stud for the valve core also consists of two identical stud segments derived by dividing, especially cutting the mount stud into two halves of identical shape along the median plane of the valve core.
  • the stud segments have abutting faces undercut at equal angles ⁇ in mirror symmetric arrangement as against the common median plane of the core.
  • the mount stud segments are positioned and mounted for both, rotation and restricted tilting with respect to the median plane of the valve core, by a mounting plate inserted, in axial alignment with the valve stem, into the housing.
  • a lower end face of the mount stud of the valve core is supported by an adjustable support screw held, with hermetic seal, in a position opposite to and in axial alignment with both, the coupling aperture of the valve core and the valve stem, in a mount disc of the ball valve assembly housing.
  • Fig 1. shows, by way of example only and partly in longitudinal sectional view, a preferred embodiment of the improved ball valve assembly according to the invention
  • Fig. 2 depicts the two identical core segments of the core of the ball valve assembly of the invention in enlarged elevation seen, partly in section, from the axial direction of the thoroughfare flow port of the core,
  • Fig. 3 shows, in enlarged elevation again and partly in section, one of the core segments as seen from the common median plane MP of the core indicated in Fig. 2,
  • Fig. 4 is a sectional view of a detail of the embodiment taken along a line IV- IV indicated in Fig. 1,
  • Fig. 5A depicts in elevation the valve stem of the preferred embodiment of the ball valve assembly of Fig. 1,
  • Fig. 5B shows in elevation, a slightly alternative design of the valve stem foreseen for embodiments of the invention in which a drive means is controlled by a power actuated device
  • Fig. 6 is an enlarged view showing the valve stem head of the improved ball valve assembly in elevation, partly in section,
  • Fig. 7 shows a cross section of the valve stem head taken along a line VTI- VII indicated in Fig. 6,
  • Fig. 8 shows a cross section taken through the valve stem head and the core segments of the ball valve assembly along a line VIII- VIII as seen is Fig. 1, and
  • Figs. 9 and 10 depict, as enlarged schematic elevational views and in different axial positions characteristic for valve operation, the closed link mechanism of the improved ball valve assembly of the invention.
  • Fig 1. of the attached drawing shows, by way of example only and partly in longitudinal sectional view, a preferred embodiment of the improved ball valve assembly comprising a valve core 1 of substantially spheroid shape located for operation within a valve housing 6 having built-in valve seats 15 and a bonnet 16 including a packing gland consisting of a gland lining 18 and a gasket retainer plug 19.
  • the valve core 1 has a thoroughfare flow port 2, and is provided with sealing smfaces capable of establishing and maintaining a tight seal against said built-in valve seats 15 of the housing 6.
  • valve core 1 in enlarged elevation, partly in section from two different directions of view perpendicular to each other
  • the valve core 1 consists of two separate core segments 1' and 1" derived by cutting the valve core 1 of substantially spheroid shape into two halves of identical shape along its median plane MP incorporating the longitudinal axis of the thoroughfare flow port 2.
  • the valve core 1 is further provided with a coupling aperture 4 and, in a position diametrically opposite to the latter, with a substantially cylindrical radial mount stud 3.
  • the mount stud 3 of the valve core 1 also consists of two identical stud segments 3 ' and 3".
  • the stud segments 3', 3" have abutting faces undercut at equal angles ⁇ in mirror symmetric arrangement as against the common median plane MP of the valve core 1.
  • the mount stud segments 3', 3" are positioned and mounted for both, synchronous co-rotation at an angle of substantially 90° in both senses of rotation around their common axis and restricted synchronous tilting relative to each other towards and away from the common median plane MP of the valve core 1 and thus, the valve seats 15, by a mounting plate 27 inserted, in axial alignment with the bonnet 16, into the housing 6.
  • a lower end face of the mount stud 3 of the valve core 1 is supported by an adjustable support screw 28 held, with he ⁇ netic seal, in a position opposite to and in axial alignment with both, the coupling aperture 4 of the valve core 1 and the bonnet 16, within a mount disc 17 of the ball valve assembly housing 6.
  • the improved ball valve assembly of the invention is shown in its closed status in which the core 1 is turned and stays in a position in which the axis of the thoroughfare flow port 2 is perpendicular to the direction of flow through the housing 6 of the valve assembly, and the core segments 1', 1" are mechanically wedged tightly against the built-in valve seats 15 of the housing 6 of the ball valve assembly, whereby a he ⁇ netic positive shut-off status of the valve is assured.
  • the ball valve assembly of the invention further comprises a valve stem 12 that is arranged diametrically opposite to and in axial alignment with the mount stud 3 of the valve core 1.
  • the valve stem 12 has a first, lower stem end portion facing the valve core 1, and an second, upper stem end portion which is coupled to a drive means capable of moving, in the embodiment shown by example in Fig. 1 by manual actuation, the valve stem 12 within the bonnet 16 in both axial directions towards and away from the valve core 1.
  • a drive means suitable for manual ball valve actuation is provided for.
  • the drive means comprises a spindle nut 23 mounted for rotation by means a pair of bearings capable of taking up axial l ⁇ ad.
  • the bearings are held at fixed axial position between the bonnet 16 and a bearing cover 21 secured by means of screw bolts to the bonnet 16 in axial alignment with the latter.
  • a handweel 24 is keyed to the spindle nut 23 the threaded inner bore of which co-operates with a co ⁇ espondingly threaded upper end portion of the valve stem 12.
  • a rod-like position indicator 29 showing the actual axial position of the valve stem 12 is anchored in the upper end portion of the valve stem 12 and extends in sealed manner through a central bore of the cup shaped spindle nut 23.
  • the valve stem 12 is associated with a mechanism for turning the valve stem 12 at angles of substantially 90° in one or the other sense of rotation when upon actuation, the drive means causes the valve stem 12 to axial movement in the one or the other direction, respectively.
  • the mechanism for turning valve stem 12 at angles of substantially 90° in one or the other sense of rotation consists of two opposite spiral grooves 13a, 13b featured on the outer smface of the valve stem 12, and of two driving pins 22a and 22b in a mounting socket 20 of fixed position relative to the housing 6.
  • the driving pins 22a, 22b co-operate with the spiral grooves 13 a and 13b of the valve stem 12, when the latter is moved between them in either axial direction.
  • valve stem 12 is received and guided in a manner allowing both, its rotation and axial movement within the mounting socket 20 which is, as a co-axial component part, secured to the bonnet 16 of the housing 6.
  • the driving pins 22a, 22b are seated and securely held in distant parallel transverse bores of the mounting socket 20.
  • Fig. 5 A shows a valve stem 12 of the improved ball valve assembly of Fig. 1 in enlarged elevation. It can be seen that both spiral grooves 13a and 13b consist of groove sections 13', 13" and 13'".
  • the two outermost groove sections 13' and 13'" of each spiral groove 13a, 13b are shaped as perpendicular flat areas of substantial axial length lying parallel with the longitudinal axis of the valve stem 12. They are interconnected by a twisted quarter turn shaped intermediate groove section 13", whereby the valve stem 12 is caused during the axial travel of the intermediate groove sections 13" of the spiral grooves 13a, 13b between the fixed driving pins 22a, 22b to a substantially 90° rotation around its longitudinal axis.
  • the valve stem 12 shown in Fig. 5A is of the design has a threaded upper end portion and is used, in association with drive means comprising a spindle nut 23 which is rotated by a handwheel 24, for manual valve actuation.
  • Fig. 5B shows a slightly modified design of a valve stem 12 which only differs from that shown in Fig. 5 A in that its upper end portion is, instead of having a thread, of a stepped shape.
  • This design is recommended in embodiments of the improved ball valve assembly in which a pneumatic or hydraulic drive means is used for valve actuation.
  • Known power actuated devices, especially such as air or hydraulic cylinders can be easily connected via suitable coupling means to the stepped upper end portion of a valve stem 12 shown in Fig. 5B.
  • the improved ball valve assembly of the invention is further provided with a valve stem head 10 that is secured rigidly to the lower end portion of the valve stem 12.
  • the valve stem head 10 has an upper head portion of substantially cylindrical shape and a lower head portion of substantially rectangular cross section.
  • the upper head portion of the valve stem head 10 is provided with a central blind bore 7 and a transverse bore 9 for receiving and rigidly securing, via a transverse coupling bolt 25 fitted into both, said transverse bore 9 and a co ⁇ esponding ti-ansverse bore 14 of the valve stem 12, the valve stem head 10 to the lower end portion of valve stem 12.
  • the upper head portion of the valve stem head 10 further comprises a protruding annular bevel face rim 8 around the circumference of the central blind bore 7.
  • the valve stem head 10 When, in the open status of the improved ball valve assembly, the valve stem head 10 a ⁇ ives at and stays in its uppermost axial position, the annular bevel face rim 8 abuts on and is pressed by the fluid pressure against an annular shoulder 30 within the inner bore of the bonnet 16 whereby the upper space regions receiving means and functional component parts used and serving for a controlled actuation of the valve assembly only, are separated under a metal-on-metal hermetic seal from the inside region of the valve housing 6 in which the core 1 is mounted for operation.
  • valve stem head 10 co ⁇ esponds in cross section with that of the coupling aperture 4 of valve core 1.
  • the valve stem head 10 is a ⁇ anged, at least partially, within the coupling aperture 4 of the valve core 1 in which it is allowed of longitudinal movement in both axial directions only. Because the cross-section of rectangular shape of both, the valve stem head 10 and the coupling aperture 4, rotations of the valve stem 12 and thus, the valve stem head 10 result in synchronous co-rotations of the core segments 1', 1" in both senses of turn.
  • the core segments 1' and 1" are mounted on the valve stem head 10 by means of a closed link mechanism which is capable of symmetrically and synchronously moving, in the closed status of the valve assembly, the core segments 1' and 1" towards and away from their built-in valve seats 15, respectively, when the valve stem 12 is caused by its drive means to additional longitudinal movement in the one or the other axial direction.
  • the closed link mechanism coupling the core segments 1', 1" and the valve stem head 10 consists of guide slots 11a and l ib in the valve stem head 10 shown, in enlarged elevation and partly in section again, in Figs. 6 and 7 of the attached drawing, and a pair of guide pins 26a, 26b seated and secured in respective bores 5' and 5" (shown in Figs.
  • each guide slot 11a, l ib are lying in minor symmetric arrangement as against the common median plane MP of the valve core 1, and each guide slot 11a, lib consists of two adjoining slot sections, namely a lower slot section substantially parallel to, and an upper slot section inclined at an angle ⁇ in respect to and away from the common median plane MP of the valve core 1.
  • Fig. 8 illustrates that the guide pins 26a, 26b pass, respectively, through the guide slots 11a and l ib of the valve stem head 10, whereby, as it will be more readily understood in from the detailed description of Figs.
  • up and down axial movements of the valve stem head 10 are converted, determined by the actual shape of the guide slots 11a and l ib, into relative movements of the core segments away and towards each other and against the built- in valve seats 15 within the housing 6 of the improved ball valve assembly of the invention.
  • Figs. 9 and 10 illustrate the operation principle of the closed link mechanism of the improved ball valve assembly of the invention.
  • the closed link mechanism is shown in a phase of operation in which, coiTesponding to what is illustrated in Fig. 1, in a previous phase of valve operation, for closing the path of flow of the fluid through the valve, the core 1 had first been turned by the mechanism consisting of the spiral grooves 13a and 13b and the driving pins 22a and 22b as dealt with in detail further above, in a position in which the axis of the thoroughfare flow port 2 is perpendicular to the direction of flow through the housing 6. Following this, by additional actuation of the valve stem 12 in downward axial, direction indicated in Fig.
  • the valve stem head 10 had been lowered into its lowermost axial end position.
  • the guide pins 26a, 26b anchored in the core segments 1' and 1" respectively were forced to slide along their respective guide slots 11a and l ib, and during their relative movement within the upper slot sections of guide slots 1 la and 1 lb inclined at an angle ⁇ away from the common median plane MP of core 1, the core segments 1', 1" were mechanically wedged tightly against the built-in valve seats 15 of the housing 6 whereby a hermetic positive shut-off status of the valve is assured.
  • Fig. 10 of the attached drawing illustrates that in a first operational phase of reversing the ball valve assembly in its open thoroughfare status of normal operation, actuated by valve stem 12, the valve stem head 10 was moved in upward axial direction as indicated by arrow B.
  • the guide pins 26a and 26b slid along and airived in their positions within the lower slot sections of their respective guide slots 11a and lib as shown in Fig. 10.
  • the core segments 1' and 1" tilted away from their valve seats 15, and the core 1 is allowed to subsequent free rotation to its full-open position without seal rubbing and wear.
  • valve stem 12 and the valve stem head 10 begin to lower.
  • the spiral grooves 13a, 13b in the valve stem 12 act against the fixed guide pins 26a, 26b, causing the valve stem 12, the valve stem head 10 and the core segments 1', 1" to rotate.
  • the handwheel 24 rotates the core segments 1', 1" a full 90° without the core segments 1', 1" touching the valve seats 15.
  • Final turns of the handwheel 24 mechanically wedge the valve stem head 10 down, pressing the core segments 1', 1" firmly against their respective valve seats 15.
  • the improved ball valve assembly embodying the invention provides for simultaneous tight seal and thus, zero leakage with full separation of the line sections of significantly different pressure values (of 40 to 60 bar) in both flow directions of the fluid.
  • the pressure loss caused by and within the valve assembly is negligible, and the free cross section of flow through the valve is practically identical with the nominal cross section of flow of the adjoining pipelines.
  • any intelligent go-pig can pass the valve without any obstacle.
  • the absence of seal nibbing during both, opening and closing, means easy, low-torque valve operation and long-term reliable performance.
  • the improved ball valve assembly of the invention is especially suitable for use within broad temperature and pressure limits in both, supply systems and calibrating systems, and also in fields of application where the fluids to be dealt with are heavily contaminated and/or co ⁇ osive substances.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Taps Or Cocks (AREA)

Abstract

L'invention concerne un ensemble de soupape de retenue à bille perfectionnée permettant d'avoir, la soupape étant fermée lors de son fonctionnement, et indépendamment de la pression de fluide existante, une étanchéité simultanée et positive dans les deux directions d'écoulement. Le noyau de soupape (1) comprend deux segments de noyau séparés (1', 1'') de forme identique, résultant de la séparation du noyau de soupape (1) de forme sensiblement sphérique, en deux moitiés, le long d'un plan médian (MP) comprenant l'axe longitudinal de l'orifice d'écoulement traversant (2) du noyau (1). Pour fermer l'ensemble de soupape selon l'invention, par rotation du volant manuel (24), la tige de soupape (12) et la tête de soupape (10) amorcent une descente. Les rainures spirales (13a, 13b) dans la tige de soupape (12) agissent à l'encontre des tiges de guidage fixes (26a, 26b), ce qui provoque la rotation de la tige de soupape (12), de la tête de soupape (10) et des segments de noyau (1', 1''). Si l'on continue de tourner le volant manuel (24), les segments de noyau (1', 1'') tournent de 90°, sans que les segments de noyau (1', 1'') viennent en contact avec les sièges de soupape (15). Lors de la rotation complète du volant (24), la tête de soupape (10) est serrée vers le bas, ce qui a pour effet de presser les segments de noyau (1', 1'') contre leurs sièges de soupape respectifs (15). En tournant le volant (24) dans le sens opposé, avant que l'ensemble de soupape à bille commence à s'ouvrir, les segments de noyau (1', 1'') pivotent à partir de leurs sièges de soupape (15). Les segments de noyau (1', 1'') tournent alors en position d'ouverture complète sans frottement ni usure, et tout en maintenant l'étanchéité.
PCT/HU2004/000013 2003-02-27 2004-02-16 Ensemble de soupape de retenue a bille WO2004076896A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
HU0300510A HU225807B1 (en) 2003-02-27 2003-02-27 Double acting ball valve
HUP0300510 2003-02-27

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WO2004076896A1 true WO2004076896A1 (fr) 2004-09-10

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2172681A1 (fr) * 2008-10-06 2010-04-07 VAT Holding AG Soupape dotée d'un obturateur rotatif
CN103511656A (zh) * 2013-09-26 2014-01-15 岳廷 分段阀杆式无摩擦球阀
CN103711933A (zh) * 2013-12-31 2014-04-09 上海凯工阀门有限公司 上装式双密封三分球阀
CN103982672A (zh) * 2014-05-29 2014-08-13 挺宇集团有限公司 一种收缩式低摩擦球阀
CN107035913A (zh) * 2017-05-12 2017-08-11 刘权 中控过滤锁控球阀
CN110778749A (zh) * 2019-11-13 2020-02-11 广东伟创科技开发有限公司 一种应用于水质自动在线监测的流路选择阀
CN112128410A (zh) * 2019-06-24 2020-12-25 杭州三花研究院有限公司 流体管理组件
CN112648403A (zh) * 2020-12-24 2021-04-13 何飞 一种先导式电磁球阀

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2277975A (en) * 1941-01-31 1942-03-31 Alfred G Heggem Valve
US2729421A (en) * 1952-12-16 1956-01-03 Sr Walter S Baer Cam-locked valve
US3515371A (en) * 1966-06-06 1970-06-02 Orbit Valve Co Valve and valve seat

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2277975A (en) * 1941-01-31 1942-03-31 Alfred G Heggem Valve
US2729421A (en) * 1952-12-16 1956-01-03 Sr Walter S Baer Cam-locked valve
US3515371A (en) * 1966-06-06 1970-06-02 Orbit Valve Co Valve and valve seat

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2172681A1 (fr) * 2008-10-06 2010-04-07 VAT Holding AG Soupape dotée d'un obturateur rotatif
CN103511656A (zh) * 2013-09-26 2014-01-15 岳廷 分段阀杆式无摩擦球阀
CN103511656B (zh) * 2013-09-26 2015-10-28 岳廷 分段阀杆式无摩擦球阀
CN103711933A (zh) * 2013-12-31 2014-04-09 上海凯工阀门有限公司 上装式双密封三分球阀
CN103711933B (zh) * 2013-12-31 2016-06-08 上海凯工阀门有限公司 上装式双密封三分球阀
CN103982672A (zh) * 2014-05-29 2014-08-13 挺宇集团有限公司 一种收缩式低摩擦球阀
CN107035913A (zh) * 2017-05-12 2017-08-11 刘权 中控过滤锁控球阀
CN112128410A (zh) * 2019-06-24 2020-12-25 杭州三花研究院有限公司 流体管理组件
CN112128410B (zh) * 2019-06-24 2022-06-24 浙江三花智能控制股份有限公司 流体管理组件
CN110778749A (zh) * 2019-11-13 2020-02-11 广东伟创科技开发有限公司 一种应用于水质自动在线监测的流路选择阀
CN112648403A (zh) * 2020-12-24 2021-04-13 何飞 一种先导式电磁球阀

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HU225807B1 (en) 2007-09-28
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