WO2013182318A1 - Dispositif à vérin différentiel servant à un entraînement hydromécanique pour un disjoncteur de puissance électrique - Google Patents

Dispositif à vérin différentiel servant à un entraînement hydromécanique pour un disjoncteur de puissance électrique Download PDF

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Publication number
WO2013182318A1
WO2013182318A1 PCT/EP2013/001676 EP2013001676W WO2013182318A1 WO 2013182318 A1 WO2013182318 A1 WO 2013182318A1 EP 2013001676 W EP2013001676 W EP 2013001676W WO 2013182318 A1 WO2013182318 A1 WO 2013182318A1
Authority
WO
WIPO (PCT)
Prior art keywords
damping
pressure
piston
pressure region
differential cylinder
Prior art date
Application number
PCT/EP2013/001676
Other languages
German (de)
English (en)
Inventor
Thomas Klose
Claus Sticker
Thomas Brenneis
Original Assignee
Abb Technology 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 Abb Technology Ag filed Critical Abb Technology Ag
Priority to DE112013002841.7T priority Critical patent/DE112013002841A5/de
Publication of WO2013182318A1 publication Critical patent/WO2013182318A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/222—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston with a piston extension or piston recess which throttles the main fluid outlet as the piston approaches its end position
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H33/00—High-tension or heavy-current switches with arc-extinguishing or arc-preventing means
    • H01H33/02—Details
    • H01H33/28—Power arrangements internal to the switch for operating the driving mechanism
    • H01H33/30—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator
    • H01H33/34—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator hydraulic

Definitions

  • the invention relates to hydraulic differential cylinder arrangement for hydromechanical drives for electrical circuit breakers.
  • Hydromechanical spring accumulator drives usually have differential cylinders.
  • a piston of the differential cylinder is connected to a piston rod which is movable by pressurizing a pressure volume.
  • the piston rod is connected to an electrical power switch, so that by moving the piston rod of the electric power switch can be switched.
  • the pressure volume of the differential cylinder can be acted upon by a hydraulic pressure, so that the piston rod moves in a corresponding position.
  • the pressure in the printing volume is usually provided by a printing cylinder which is coupled to a mechanical energy storage, such as a spring assembly. If the circuit breaker to be switched, the spring force is released to the pressure cylinder, so that there builds a working or system pressure, which is present via a hydraulic connection in the pressure volume of the differential cylinder. Due to the working pressure in the
  • CONFIRMATION COPY Pressure range are moved to the piston and the piston rod of the differential cylinder.
  • the mechanical energy store is formed on the pressure cylinder as a spring arrangement, this is usually applied to provide a sufficient force with a bias voltage.
  • the working pressure builds up very quickly, so that the pressure range of the differential cylinder is applied almost directly to the working pressure.
  • the piston of the differential cylinder is moved with a high acceleration force in the direction of an end stop.
  • a cushioning is often provided in which the speed of the piston is reduced before this or another component strikes against a stop.
  • the damping is intended to cause the final speed of the piston is brought below a predetermined threshold when striking, in order to avoid damage to the components.
  • hydromechanical spring-loaded drives are already set at the beginning of production to a specific application. A change in the scope is usually no longer possible after their production. This makes the production of hydromechanical spring storage drives inflexible, since they can only be made specifically for a particular application and it is not possible to produce for a number of indefinite applications on stock and adapt after their preparation to the given application.
  • hydromechanical spring accumulator drive which has an end position damping which can be decelerated regardless of the working pressure provided by the mechanical energy accumulator and regardless of the mass moved with the piston rod such that a terminal speed of the piston rod is below a predetermined threshold is achieved before the piston, the piston rod or an associated component abuts an end stop.
  • a differential cylinder arrangement for a hydromechanical drive for actuating an electrical switch, in particular a high-voltage switch, is provided.
  • the differential cylinder assembly includes:
  • a movable piston in a range of movement movable in response to a pressure difference between the first and second pressure ranges
  • a damping device which provides during a movement of the piston in the direction of the second pressure region, an attenuation, also called cushioning, against the movement of the piston, wherein the damping automatically sets, and the damping means a damping chamber at an opposite end of the piston second pressure region and a protruding on the piston in the direction of the second pressure region cylindrical, in particular circular cylindrical, damping pin wherein the damping pin and the damping chamber are formed so that the damping pin protrudes in a movement range in the damping chamber and thus separates the second pressure range from the damping chamber.
  • the damping device comprises a damping bush, in the interior of which the damping chamber forms a third pressure region, which can be closed by at least one movable closure element.
  • the movable with the damping chamber cooperating closure element is movable during a movement of the piston by means of a contact pressure of at least one cooperating plate spring.
  • three parts which are movable in the axial direction, in particular closure pins, are provided as closure elements.
  • the damping chamber and the second pressure region are connectable via at least one hydraulic line with a hydraulic fluid container, for example by means of a 3/2-way seat valve.
  • hydrostatic-mechanical differential cylinder assembly provides damping of movement of the piston in a portion (portion) of the range of movement of the piston to reduce the speed of the piston prior to reaching an end stop.
  • the differential cylinder arrangement hereinafter also referred to as a differential cylinder, regardless of the knowledge of the later system in which it is used.
  • the damping pin and the damping chamber are formed so that after the penetration of the damping pin in the damping chamber remains a residual gap having a predetermined passage cross-section.
  • the predetermined passage cross-section can be chosen so that this causes a predetermined maximum damping against the movement of the piston.
  • the third pressure region experiences a separation from the second pressure region through the damping pin.
  • the hydraulic fluid initially flows only through the residual gap in the second pressure range and then back into the hydraulic fluid reservoir, wherein the damping pressure resulting from this congestion in the third pressure range brakes the differential piston.
  • the closure element moves away with its guide from the bottom of the damping bushing, as soon as the damping pressure in the third pressure range exerts a greater force on the closure element, as the contact pressure of the provided disc springs and an additional connection between the third pressure region and the second pressure region is formed, through which the hydraulic fluid flows in the third pressure range.
  • the closure element again presses against the bottom of the damping bushing as soon as the damping pressure in the third pressure region decreases again and the contact force of the disk springs exceeds the pressure force exerted on the closure element and the additional connection between the third pressure region and the second pressure region closes again, as a result Height of the pressure in the third pressure range regulates and thus the braking effect on the differential piston.
  • the movable closure element thus advantageously controls the damping pressure.
  • opening pressure The pressure at which the hydraulic force on the closure element (pressure times effective area) is equal to the closing spring force and therefore opens the closure element.
  • opening pressure is determined by the ratio of the force of the disc springs used to the effective surface of the closure element.
  • the active surface is the acted upon by the damping pressure circular area of the closure element within the contact and sealing point between the closure element and damping bushing.
  • a hydromechanical drive is provided with the above differential cylinder, which is preferably used in high-voltage circuit breakers.
  • Fig. 1 is a schematic cross-sectional view through a hydraulic
  • Differential cylinder with a cushioning shows a schematic cross-sectional view of a hydraulic differential cylinder 1 with a piston 2, which separates a first pressure region 3 from a second pressure region 4, 5.
  • the piston 2 is movably arranged in a cylinder interior, wherein the piston 2 hermetically separates the first and the second pressure region 3, 4, 5 from each other.
  • the first pressure range 3 can be acted upon by a working or system pressure p1.
  • the working pressure p1 may be provided, for example, by a separate pressure cylinder (not shown) which may be caused by the release of a mechanical energy accumulator, such as a biased plate or coil spring, onto a piston 2 of the pressure cylinder.
  • a mechanical energy accumulator such as a biased plate or coil spring
  • the hydraulic differential cylinder 1 serves to provide a release movement.
  • the piston 2 of the differential cylinder 1 is connected to a piston rod 6, which causes as an actuator directly or indirectly opening or closing, for example, an electrical high voltage or medium voltage circuit breaker.
  • the piston 2 moves in accordance with the pressure difference between the first and second pressure ranges 3, 4, 5 so that the volume of the second pressure range 4, 5 decreases, one in the second pressure range 4, 5 located hydraulic fluid via a designated hydraulic line 7 directly or indirectly flows into a hydraulic fluid reservoir (not shown) and therefore exerts no significant back pressure on the piston 2.
  • the hydraulic line 7 is preferably connected via a 3/2-Wegevewntil with a hydraulic fluid reservoir.
  • the piston 2 of the differential cylinder 1 Upon initiation of the hydromechanical drive, the piston 2 of the differential cylinder 1 is accelerated, wherein the second pressure range 4, 5 does not contribute significantly to reducing the speed of the piston 2. In this way, a switching operation carried out with the aid of the hydromechanical drive can be carried out at a desired speed, so that fast tripping operations are possible. It should be avoided that the accelerated by the triggering process piston 2 of the differential cylinder 1 or a component connected thereto strikes unchecked at an end stop, as this can be damaged and also disturbing noises can occur. For this reason, a cushioning is provided. For the cushioning of the hydraulic differential cylinder 1 with a cylindrical, in particular circular cylindrical, damping pin 10 is provided, which causes a damping of the movement of the piston 2 during movement of the piston 2.
  • a damping bushing 12 in whose interior a damping chamber 11 and a third pressure range is formed, and cooperating, preferably designed as a closure pin closure elements 15 and 17 provided one or more disc springs, wherein the closure pin or 15 by means of a contact force of it cooperating disc springs 17 are movable.
  • the differential piston 2 moves uniformly driven by the first pressure range 3 with a system pressure p1 to the end position damping.
  • the case displaced hydraulic fluid in the second pressure range 4, 5 can flow directly into the hydraulic line 7, therefore, is almost unpressurized and does not contribute to the braking of the differential piston 2 at.
  • the damping pin 10 extends into a damping space 11 situated below the damping pin 10, also referred to as a damping chamber or third pressure region, the third pressure region 11 is cut off from the hydraulic line 7.
  • the opening pressure is determined by the ratio of the cup spring force to the active surface 16 of the closure pin 15.
  • the damping chamber 11 and the damping pin 10 have cross-sections which, when the damping pin 10 penetrates into the damping chamber 11, leave a residual gap 8 through which hydraulic fluid can escape from the damping chamber 11 into the second pressure region 4, 5. In this way, a throttle action is realized by the residual gap 8, since the trapped in the damping chamber 11 hydraulic fluid can only pass over the residual gap 8 in the second pressure range 4 and thus via the hydraulic line 7 in the hydraulic fluid reservoir.
  • the hydraulic line 7 for discharging the hydraulic fluid from the second pressure region 4, 5 is thus no longer in direct fluid communication with the hydraulic fluid trapped in the damping chamber 11 except for the residual gap 8.
  • the cross section of the damping pin 10 is smaller than the cross section of the damping chamber 11 is formed to ensure the residual gap 8 for the passage of hydraulic fluid.
  • the effective passage cross section of the residual gap can be selected so that an attenuation of the movement of the piston 2 is made possible with a maximum adjustable damping.
  • the maximum adjustable damping can be predetermined, for example, in the design of the hydraulic drive.
  • the closing element 15, as it moves through the provided disc springs 17, advantageously alters the cross section through which the hydraulic fluid in the third pressure region 1 can flow via the hydraulic line 7, thereby preventing a further increase in the pressure p3.
  • the movable closure element 15 and released by this cross-section act as a check valve with spring bias and cause a damping of the piston 2 automatically sets, so that the differential cylinder can be made application independent.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Damping Devices (AREA)
  • Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)

Abstract

L'invention concerne un dispositif à vérin différentiel (1) servant à un entraînement hydromécanique pour l'actionnement d'un interrupteur électrique, en particulier d'un disjoncteur à haute tension, comprenant une première zone de pression (3) destinée à être sollicitée par une pression de fonctionnement (p1); une deuxième zone de pression (4, 5); un piston (2) mobile dans une zone de déplacement, qui est déplaçable en fonction d'une différence de pression entre la première zone de pression et la deuxième zone de pression (3, 4, 5); un dispositif d'amortissement qui produit, lors d'un déplacement du piston (2) en direction de la seconde zone de pression (4, 5), un amortissement à l'encontre du piston (2), l'amortissement s'autorégulant, et le dispositif d'amortissement présentant une chambre d'amortissement (11), à une extrémité de la deuxième zone de pression (4), opposée au piston (2), et un pivot d'amortissement (10), faisant saillie, au niveau du piston (2), en direction de la deuxième zone de pression, le pivot d'amortissement (10) et la chambre d'amortissement (11) étant configurés de façon que le pivot d'amortissement (10) émerge dans une zone de mouvement, dans la chambre d'amortissement (11) et, de ce fait, sépare la deuxième zone de pression (4, 5) de la chambre d'amortissement (11). Le dispositif d'amortissement présente un manchon d'amortissement (12), dans l'espace intérieur duquel, la chambre d'amortissement (11) forme une troisième zone de pression, qui peut être fermée par au moins un élément de fermeture mobile (15), et l'élément de fermeture mobile (15) qui coopère avec la chambre d'amortissement (11) pouvant être déplaçable, lors d'un déplacement du piston (2), au moyen d'une force de pression exercée par au moins une rondelle-ressort (17) qui coopère avec.
PCT/EP2013/001676 2012-06-08 2013-06-07 Dispositif à vérin différentiel servant à un entraînement hydromécanique pour un disjoncteur de puissance électrique WO2013182318A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112013002841.7T DE112013002841A5 (de) 2012-06-08 2013-06-07 Differentialzylinderanordnung für einen hydromechanischen Antrieb für elektrische Leistungsschalter

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012011498A DE102012011498A1 (de) 2012-06-08 2012-06-08 Differentialzylinderanordnung für einen hydromechanischen Antrieb für elektrische Leistungsschalter
DE102012011498.2 2012-06-08

Publications (1)

Publication Number Publication Date
WO2013182318A1 true WO2013182318A1 (fr) 2013-12-12

Family

ID=48577682

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2013/001676 WO2013182318A1 (fr) 2012-06-08 2013-06-07 Dispositif à vérin différentiel servant à un entraînement hydromécanique pour un disjoncteur de puissance électrique

Country Status (2)

Country Link
DE (2) DE102012011498A1 (fr)
WO (1) WO2013182318A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111566337A (zh) * 2018-01-11 2020-08-21 罗伯特·博世有限公司 用于配量流体的阀

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS49339U (fr) * 1972-04-07 1974-01-05
JPS5723683Y2 (fr) * 1974-11-08 1982-05-22
JPS62224706A (ja) * 1986-03-25 1987-10-02 Maruzen Sewing Mach Co Ltd 流体圧シリンダ
EP0617202A1 (fr) * 1993-02-22 1994-09-28 Fibro GmbH Dispositif amortisseur de fin de course pour un système mobile
JP2000195391A (ja) * 1998-12-28 2000-07-14 Hitachi Ltd 遮断器の流体圧駆動装置
JP2002133982A (ja) * 2000-10-27 2002-05-10 Hitachi Ltd 遮断器の流体圧駆動装置

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3123169A1 (de) * 1981-06-05 1982-12-23 Siemens AG, 1000 Berlin und 8000 München Hydraulische betaetigungsvorrichtung fuer hochspannungs-leistungsschalter
DE4114630A1 (de) * 1991-04-30 1992-11-05 Siemens Ag Hochspannungs-leistungsschalter mit ausschaltdaempfung

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS49339U (fr) * 1972-04-07 1974-01-05
JPS5723683Y2 (fr) * 1974-11-08 1982-05-22
JPS62224706A (ja) * 1986-03-25 1987-10-02 Maruzen Sewing Mach Co Ltd 流体圧シリンダ
EP0617202A1 (fr) * 1993-02-22 1994-09-28 Fibro GmbH Dispositif amortisseur de fin de course pour un système mobile
JP2000195391A (ja) * 1998-12-28 2000-07-14 Hitachi Ltd 遮断器の流体圧駆動装置
JP2002133982A (ja) * 2000-10-27 2002-05-10 Hitachi Ltd 遮断器の流体圧駆動装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111566337A (zh) * 2018-01-11 2020-08-21 罗伯特·博世有限公司 用于配量流体的阀
US11698049B2 (en) 2018-01-11 2023-07-11 Robert Bosch Gmbh Valve for metering a fluid

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Publication number Publication date
DE112013002841A5 (de) 2015-03-05
DE102012011498A1 (de) 2013-12-12

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