EP2740135B1 - Cylindre différentiel pour un entraînement hydromécanique d'interrupteurs de puissance électriques - Google Patents

Cylindre différentiel pour un entraînement hydromécanique d'interrupteurs de puissance électriques Download PDF

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Publication number
EP2740135B1
EP2740135B1 EP12743078.3A EP12743078A EP2740135B1 EP 2740135 B1 EP2740135 B1 EP 2740135B1 EP 12743078 A EP12743078 A EP 12743078A EP 2740135 B1 EP2740135 B1 EP 2740135B1
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EP
European Patent Office
Prior art keywords
piston
damping
pressure
damping chamber
control
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.)
Active
Application number
EP12743078.3A
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German (de)
English (en)
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EP2740135A1 (fr
Inventor
Thomas Brenneis
Matthias Schmidt
Henrik Lohrberg
Frank Fiedler
Bruno Gehlert
Roland Palm
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ABB Schweiz AG
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ABB Schweiz AG
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Publication of EP2740135A1 publication Critical patent/EP2740135A1/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
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H3/00—Mechanisms for operating contacts
    • H01H3/60—Mechanical arrangements for preventing or damping vibration or shock
    • H01H3/605—Mechanical arrangements for preventing or damping vibration or shock making use of a fluid damper
    • 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 cylinders 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 pressure, which is present via a hydraulic connection in the pressure volume of the differential cylinder. The working pressure in the pressure range moves 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.
  • a separate geometric design of the damping must be carried out individually for each application.
  • the hydromechanical spring-loaded drives are already set at the beginning of production to a specific application.
  • the US 3,885,454 describes a hydraulically operated drive for a circuit breaker in which a hydraulic high-pressure accumulator provides the energy required for switching, wherein the pressure in the high pressure accumulator is maintained by a pump.
  • the drive includes a differential cylinder with cushioning as described above for hydromechanical spring drives, wherein the piston has a pin-shaped end which penetrates through the piston into a bore before reaching the end stop. The hydraulic fluid can then escape only through a bypass line with adjustable cross-section, whereby a damping is achieved.
  • hydromechanical spring accumulator drive which has an end position damping, regardless of the mechanical Energy stored working pressure and regardless of the mass moved with the piston rod can be braked so that a final speed of the piston rod is reached below a predetermined threshold before the piston, the piston rod or an associated component abuts an end stop.
  • hydro-mechanical drive differential cylinder 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.
  • an adjustable damping it is possible to form the differential cylinder independently of the knowledge of the later system in which it is used. The damping is set only when the desired damping is known, which should experience the piston before hitting a stop. In this way, a largely application-neutral production of such hydromechanical drives is possible, which can be done without knowledge of the final application.
  • the damping device has a damping chamber at an end of the second pressure region opposite the piston and a damping journal projecting on the piston in the direction of the second pressure region, wherein the damping journal and the damping chamber are designed such that the damping journal is in a section of the movement region into the damping chamber protrudes and thus separates the second pressure range of the damping chamber. It can thereby be achieved that in a first portion of the range of movement of the piston no appreciable damping is caused. Only in a second portion of the movement range, when the damping pin passes through the movement of the piston in a damping chamber, the fluid contained in the damping chamber is enclosed, so that it can flow out of the damping chamber only by a reduced passage cross-section.
  • the cross section through which the hydraulic fluid can flow out of the damping chamber is adjustable, so that the hydromechanical drive on the Use case, that is, on the output speed of the piston, the force acting on the piston, the maximum speed of the piston and the mass of the piston rod connected to the elements, adjustable to achieve the desired switching behavior of the operated with the hydro-mechanical drive circuit breaker.
  • 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 damper chamber may include one or more exhaust ducts each closed or open by the damper pin depending on the position of the damper pin in the damper chamber, the outlet ducts being connected to adjustable throttle units via connecting ducts to establish a passage area for a hydraulic fluid in the damper chamber.
  • an adjusting unit can be provided in order to set the passage cross sections of the throttle units together.
  • the damping chamber may be arranged in a movable damping piston which is movable in the direction of a third pressure range, so that depending on a pressure in the damping chamber, the damping piston moves in the direction of the third pressure range, so that an increase in pressure in the damping chamber is limited ,
  • a pressure equalization line be provided between the damping chamber or the damping pin and a volume connected to the second pressure range, wherein in the pressure equalization line, a valve is provided to allow only an inflow of hydraulic fluid into the damping chamber.
  • FIG. 1 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.
  • the piston 2 is movably arranged in a cylinder interior 5, wherein the piston 2 hermetically separates the first and the second pressure region 3, 4 from each other.
  • the first pressure region 3 can be acted upon by a working pressure.
  • the working pressure 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 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 of an electrical circuit breaker.
  • the piston 2 Upon application of the working pressure in the first pressure range 3, the piston 2 moves according to the pressure difference between the first and the second pressure region 3, 4 so that the volume of the second pressure region 4 decreases, wherein the hydraulic fluid in the second pressure region 4 on the Hydraulic line 7 flows directly into a hydraulic fluid reservoir (not shown) and therefore exerts no significant back pressure on the piston 2.
  • 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 region 4 does not contribute to reducing the speed of the piston 2. In this way, with the help of the hydromechanical drive switching operation with a desired speed are performed so that fast tripping operations are possible.
  • the cushioning is formed in this embodiment by means of a cylindrical, in particular circular cylindrical, damping pin 10, which is passive during a movement of the piston 2 in a range B of the interior 5 and damping the movement of the piston 2 causes as soon as the piston 2 at further Reduction of the volume of the second pressure region 4 in a damping region D moves.
  • the position, which represents the transition between the movement region B and the damping region D, is defined by the entry of the damping pin 10 into a likewise cylindrical damping chamber 11 when the volume of the second pressure region 4 is reduced.
  • the damping chamber 11 has a cross-section which substantially corresponds to the cross section of the damping pin 10.
  • the damping pin 10 hermetically closes off the hydraulic fluid in the damping chamber 11, for the most part hermetically against the second pressure region 4.
  • the hydraulic line 7 for discharging the hydraulic fluid from the second pressure region 4 is thus no longer in direct fluid communication with the hydraulic fluid trapped in the damping chamber 11.
  • the cross section of the damping pin 10 may be formed smaller than the cross section of the damping chamber 11, to ensure a 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 for example, in the interpretation of be predetermined hydraulic drive. So z. B. a passage cross section of 0.5% to 5% of the cross-sectional area of the damping pin 10 is possible.
  • the damper chamber 11 has a number of outlet ducts 9, which constitute connecting ducts between the damper chamber 11 and the hydraulic duct 7.
  • the outlet lines 9 each have a throttle unit 12, which represents a flow resistance for the hydraulic fluid in the outlet lines 9.
  • three outlet ducts 9 are provided with respective throttling units 12 of separately variable cross-section.
  • the outlet ducts 9 are disposed on a side wall of the damper chamber 11 with respect to the direction of movement of the damper pin 10 at axially staggered positions so that one or more of the outlet ducts 9 is controlled by the damper pin 10 (or through) depending on the position of the damper pin 10 in the damper chamber 11 the side wall of the damping pin 10) can be closed.
  • the throttle units 12 have a variable cross-section, which is individually adjustable.
  • the respective connecting lines 9, which connect the damping chamber 11 via the respective throttle unit 12 with the second pressure region 4, are with respect to the direction of movement of the damping pin 10 arranged at different axial positions. In this way, an increasing damping can be achieved, the further the damping pin 10 penetrates into the damping chamber 11. While initially in the damping region, the cross sections of the throttle units 12 allow in total the outflow of hydraulic fluid trapped in the damping chamber 11, upon further movement of the damping pin 10 access to the first connection line 9 and the corresponding throttle unit 12 is initially closed, so that only the Cross sections of the second and third throttle unit 12 can provide for the outflow of the hydraulic fluid from the damping chamber 11.
  • the check valve 15 remains when braking the movement, d. H. during a movement of the piston 2 in the direction of the damping region D, closed and only serves to ensure that the movement of the piston 2 in the opposite direction, d. H. in the direction of the movement range B, is not hindered by the damping.
  • FIG. 2 an example of a throttle unit 12 is shown with individually adjustable effective cross-sectional area.
  • a throttle sleeve 20 which is connectable at one end over the outlet 9 with the damping chamber 11.
  • a connecting line 21 is provided, which is connectable to the hydraulic line 7 or equivalent.
  • a set screw 22 is inserted inside the sleeve 20.
  • the adjusting screw 22 has a head portion 26 which is movable in the axial direction A of the throttle sleeve 20 in order to increase or decrease a passage between the outlet 9 and the connecting line 21.
  • the effective passage area can be adjusted by positioning the set screw 22.
  • the adjusting screw is provided on a head part 26 with an external thread 23.
  • the external thread 23 is in engagement with an internal thread 24, which is arranged on the sleeve 20 on a side opposite the external thread 23 area. Through the thread, the adjusting screw 23 can be adjusted by turning in the axial direction A, whereby an exact adjustment of the effective passage cross-section of the throttle unit 12 is possible.
  • a connection to the hydraulic line 7 and the hydraulic fluid reservoir is provided.
  • the actuator 31 has a cavity 37. Passages 33 in the lateral surface of the actuating element 31 connect the outer surface with the cavity 37 and the free space 37.
  • the cavity 37 and the free space 37 opens at one end of the actuating element 31, which is provided with the connection to the hydraulic line 7, frontal end associated with the sleeve-shaped recess 32.
  • the passages 33 may be slit-shaped, circular or formed as an eccentric with extending in the axial or radial direction of extension of the adjusting element 31 changing cross section.
  • the passages 33 are arranged at positions which correspond to the positions of the mouths of the outlet lines 9, so that the passages 33 partially or completely come into coincidence with the mouths of the outlet lines 9 by corresponding rotation of the adjusting element 31.
  • the degree of overlap between the mouths of the outlet conduits 9 and the passages 23 defines the effective passage area of the throttle unit thus formed.
  • FIG. 6 is a schematic cross-sectional view of another embodiment of a hydraulic differential cylinder 40 shown with end position damping.
  • a major difference between the hydraulic differential cylinder of FIG. 1 and the hydraulic differential cylinder of FIG. 7 is that the damping chamber 11 is arranged in a movable damping piston 41.
  • the damping piston 41 is movable in the same direction as the piston 2 and on one of the damping chamber 11 opposite side (third pressure range) with the working pressure or other adjustable pressure acted upon.
  • the damping chamber 11 in the damping piston 41 is in contrast to the embodiment of FIG. 1 not connected via one or more throttle units 12 with the hydraulic fluid reservoir.
  • damping pressure acts on a first control surface A 1 , which essentially has the cross-sectional area the damping chamber 11 corresponds.
  • the damping pressure causes a force on the damping piston 41.
  • the damping piston 41 moves in the damping direction, ie in the same direction in which the damping pin 10 moves.
  • the check valve 43 is provided so that it opens out of the damping area D in a movement direction of the piston 2 in a direction of movement, ie at a positive pressure gradient between the second pressure region 4 and the damping chamber 11. This embodiment allows an unobstructed movement of the piston second in direction of movement B.
  • FIG. 7 is a schematic cross-sectional view of another embodiment of a hydraulic differential cylinder 50 according to another embodiment shown.
  • the damping chamber 11 is connected via a connecting line 51 to the hydraulic line 7, which connects the second pressure region 4 with the hydraulic fluid reservoir, or directly to the second pressure region 4.
  • a control cylinder 53 is provided with a control piston 54.
  • the control piston 54 serves to create a connection between the damping chamber 11 and the second pressure region 4 or the hydraulic fluid reservoir.
  • the control piston 54 is formed as a differential piston, one side of which has a piston surface A 3 , which is exposed to the working pressure with which the piston 2 is acted on the part of the first pressure region 3, while the corresponding other side a smaller compared to control surface A first has on a provided on the control piston control pin 55 which is exposed to the pressure of the damping chamber 11.
  • the control pin 55 also serves to form a valve for the connecting line 51, wherein the passage cross-section of the valve is indicated by the position of the control piston 54. Due to the working pressure acting on the piston surface A 3 , the valve is initially closed.
  • a residual gap 56 is provided between the damping pin 10 and the damping chamber 11, which allows an escape of hydraulic fluid in the second pressure region 4 with a defined cross-section. If the damping pressure increases in the damping chamber 11, then comes It depends on the design of the control piston 54, when the control piston 54 is moved and allows the additional discharge between the damping chamber 11 to the hydraulic fluid reservoir via the connecting line 51. When the pressure in the damping chamber 11 drops, the working pressure acting on the further control surface A 3 of the control pin 55 moves the control piston 54 and causes the connecting line 51 to close.
  • the control piston 54 constitutes a self-regulating system which keeps the pressure in the damping chamber 11 constantly below a value set by the area ratio during the entire decelerating operation of the piston 2.
  • the control piston 54 furthermore has an area A 2 , to which the pressure of the hydraulic fluid in the second pressure area 4 acts in the closed state of the control valve. If the piston 2 to move in the opposite direction (by reducing the working pressure), the damping pressure in the damping chamber 11 is reduced and there is a positive pressure gradient between the second pressure region 4 and the damping chamber 11. In this case, the control piston 54 opens the complete cross-section and allows a sufficiently large flow of liquid from the hydraulic fluid line 7 in the damping chamber 11, so as not to hinder the movement of the damping pin 10 from the damping chamber 11 out. In order to ensure such functionality, it is provided that the sum of the first control surface A 1 and the second control surface A 2 exceeds the further piston surface A 3 .

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Damping Devices (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (8)

  1. Cylindre différentiel (50), destiné à un entraînement hydromécanique destiné à actionner un commutateur électrique, en particulier un commutateur à haute tension, comprenant :
    - une première zone de pression (3) destinée à être soumise à une pression de travail ;
    - une deuxième zone de pression (4) ;
    - un piston (2) qui est mobile dans une zone de mouvement et qui peut être déplacé entre les première et deuxième zones de pression (3, 4) en réponse à une différence de pression ;
    - un moyen d'amortissement étant prévu qui fournit un amortissement contre le mouvement du piston (2) dans une partie (D) de la zone de déplacement lors d'un mouvement du piston (2) en direction de la deuxième zone de pression (4), l'amortissement étant réglable, et
    - le moyen d'amortissement comportant une chambre d'amortissement (11) à une extrémité, opposée au piston (2), de la deuxième zone de pression (4) et une broche d'amortissement (10) saillant au niveau du piston (2) en direction de la deuxième région de pression (10), la section transversale de la broche d'amortissement (10) étant conçue pour être inférieure à la section transversale de la chambre d'amortissement (11) pour garantir un intervalle résiduel (8) destiné au passage du fluide hydraulique,
    caractérisé en ce que
    - un conduit de liaison (51) est prévu entre la chambre d'amortissement (11) et un volume raccordé à la deuxième zone de pression (4), une vanne étant prévue dans le conduit de liaison (51), laquelle libère une section transversale de passage en fonction d'une pression de travail fournie et d'une pression dans la chambre d'amortissement (11) pour limiter la pression dans la chambre d'amortissement (11) et une autre surface de commande (A2) étant prévue pour ouvrir la soupape lors d'une chute de pression positive entre le volume raccordé à la deuxième zone de pression (4) et la pression dans la chambre d'amortissement (11).
  2. Cylindre différentiel (50) selon la revendication 1, la broche d'amortissement (10) et la chambre d'amortissement (11) étant conçues de telle sorte que l'intervalle résiduel (8) restant après la pénétration de la broche d'amortissement (10) dans la chambre d'amortissement (11) présente une section transversale de passage prédéterminée.
  3. Cylindre différentiel (50) selon la revendication 2, la section transversale de passage prédéterminée étant choisie de manière à provoquer un amortissement maximum prédéterminé à l'encontre du mouvement du piston (2).
  4. Cylindre différentiel (50) selon l'une des revendications précédentes, la vanne étant formée par une broche de commande (55) qui est prévue au niveau d'un piston de commande (54), le piston de commande (54) étant prévu dans un cylindre de commande (53), et la section transversale de passage de la vanne étant indiquée par la position du piston de commande (54).
  5. Cylindre différentiel (50) selon la revendication 4, le piston de commande (54) étant conçu comme un piston différentiel dont un côté présente une surface de piston (A3) qui est exposée à la pression de travail à laquelle le piston (2) est également soumis dans la première zone de pression (3) tandis que l'autre côté du piston de commande (54) présente sur la broche de commande une surface de commande (A1), plus petite que la surface de piston (A3), qui est soumise à la pression de la chambre d'amortissement (11).
  6. Cylindre différentiel (50) selon la revendication 5, le piston de commande (54) formant un système autorégulateur qui maintient la pression dans la chambre d'amortissement (11), pendant toute l'opération de décélération du piston (2), constante à une valeur réglée par le rapport de la surface de piston (A3) à la surface de commande (A1).
  7. Cylindre différentiel (50) selon l'une des revendications 5 ou 6, la surface de commande (A1), qui est soumise à la pression de la chambre d'amortissement (11), formant une première surface de commande, et l'autre surface de commande (A2), sur laquelle la pression du fluide hydraulique agit dans la deuxième zone de pression (4) lorsque la vanne est fermée, formant une deuxième surface de commande et la somme de la première surface de commande (A1) et de la deuxième surface de commande (A2) dépassant la surface de piston (A3) .
  8. Entraînement hydromécanique destiné à un disjoncteur de puissance à haute tension comprenant un cylindre différentiel (50) selon l'une des revendications précédentes.
EP12743078.3A 2011-08-03 2012-07-26 Cylindre différentiel pour un entraînement hydromécanique d'interrupteurs de puissance électriques Active EP2740135B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011109210A DE102011109210B3 (de) 2011-08-03 2011-08-03 Differentialzylinder für einen hydromechanischen Antrieb für elektrische Leistungsschalter
PCT/EP2012/003167 WO2013017226A1 (fr) 2011-08-03 2012-07-26 Cylindre différentiel pour un entraînement hydromécanique d'interrupteurs de puissance électriques

Publications (2)

Publication Number Publication Date
EP2740135A1 EP2740135A1 (fr) 2014-06-11
EP2740135B1 true EP2740135B1 (fr) 2019-02-13

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ID=46604253

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EP12743078.3A Active EP2740135B1 (fr) 2011-08-03 2012-07-26 Cylindre différentiel pour un entraînement hydromécanique d'interrupteurs de puissance électriques

Country Status (6)

Country Link
US (1) US9920777B2 (fr)
EP (1) EP2740135B1 (fr)
KR (1) KR20140064762A (fr)
CN (1) CN202746323U (fr)
DE (1) DE102011109210B3 (fr)
WO (1) WO2013017226A1 (fr)

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Publication number Publication date
US9920777B2 (en) 2018-03-20
DE102011109210B3 (de) 2012-10-11
US20140137731A1 (en) 2014-05-22
EP2740135A1 (fr) 2014-06-11
KR20140064762A (ko) 2014-05-28
WO2013017226A1 (fr) 2013-02-07
CN202746323U (zh) 2013-02-20

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