EP2234135B1 - Agencement de vannes - Google Patents

Agencement de vannes Download PDF

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Publication number
EP2234135B1
EP2234135B1 EP20100002602 EP10002602A EP2234135B1 EP 2234135 B1 EP2234135 B1 EP 2234135B1 EP 20100002602 EP20100002602 EP 20100002602 EP 10002602 A EP10002602 A EP 10002602A EP 2234135 B1 EP2234135 B1 EP 2234135B1
Authority
EP
European Patent Office
Prior art keywords
valve
control
main valve
slide
main
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
EP20100002602
Other languages
German (de)
English (en)
Other versions
EP2234135A2 (fr
EP2234135A3 (fr
Inventor
Niels Wahlefeld
Matthias Schmidt
Franz-Josef Körber
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.)
ABB Technology AG
Original Assignee
ABB Technology AG
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Filing date
Publication date
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Publication of EP2234135A2 publication Critical patent/EP2234135A2/fr
Publication of EP2234135A3 publication Critical patent/EP2234135A3/fr
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Publication of EP2234135B1 publication Critical patent/EP2234135B1/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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0431—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the electrical control resulting in an on-off function
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/006—Hydraulic "Wheatstone bridge" circuits, i.e. with four nodes, P-A-T-B, and on-off or proportional valves in each link
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/022—Flow-dividers; Priority valves
    • 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
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1404—Characterised by the construction of the motor unit of the straight-cylinder type in clusters, e.g. multiple cylinders in one block
    • 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
    • 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
    • H01H33/53—Cases; Reservoirs, tanks, piping or valves, for arc-extinguishing fluid; Accessories therefor, e.g. safety arrangements, pressure relief devices
    • H01H33/55—Oil reservoirs or tanks; Lowering means therefor
    • 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
    • H01H33/53—Cases; Reservoirs, tanks, piping or valves, for arc-extinguishing fluid; Accessories therefor, e.g. safety arrangements, pressure relief devices
    • H01H33/56—Gas reservoirs
    • H01H33/561—Gas reservoirs composed of different independent pressurised compartments put in communication only after their assemblage
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet valves
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/30575—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve in a Wheatstone Bridge arrangement (also half bridges)
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7052—Single-acting output members
    • 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
    • H01H2033/308—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator comprising control and pilot 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
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87193—Pilot-actuated
    • 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
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87193—Pilot-actuated
    • Y10T137/87201—Common to plural valve motor chambers
    • 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
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87193—Pilot-actuated
    • Y10T137/87209—Electric
    • 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
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87217—Motor
    • Y10T137/87225—Fluid motor

Definitions

  • the invention relates to a valve arrangement according to the preamble of claim 1.
  • Such valve arrangements are used to control piston-cylinder arrangements.
  • the piston is located at one end of a piston rod, so that the cross-sectional area of the space above the piston is greater than the cross-sectional area below the piston, since in this cross-sectional area, the cross-sectional area of the piston rod comes to trigger.
  • the piston moves in a first direction because the force exerted on the top of the piston by the high pressure fluid is greater than the force applied to the bottom of the piston because of the larger cross sectional area.
  • a low pressure reservoir also called a low pressure tank
  • the piston moves in a direction opposite to the first direction.
  • the piston rod is therefore extended upon application of space above the piston from the cylinder and retracted again during unloading.
  • the medium is any fluid in question. Usually, hydraulic oil or in some cases also compressed air is used.
  • the hydraulic oil can from certain high pressure tanks are provided, the structure of which is not relevant to the present invention.
  • Such piston cylinder arrangements are used in particular for actuating the movable contact piece of high-voltage circuit breakers, of course, can also be used in other applications in which components such. As crane arms, blades of shovels and the like to be moved.
  • the DE 2047 838 A1 shows a high voltage electrical power actuator, because it is operated by a hydraulic drive.
  • two valves are controlled by electromagnets which cooperate with a pilot valve and a main valve.
  • connection of the space or- and below the piston with the high-pressure tank as well as the connection of the space above the piston with the low-pressure tank or with other connections is effected by means of mostly electrically controlled valves, with a 3/2-way valve or two 2/2 Directional valves, which operate independently of each other, is used or will.
  • the object of the invention is to provide a valve arrangement of the type mentioned, in which the above-mentioned requirements can be met at low production costs with low Um Kunststoffbuchneren.
  • the invention is characterized in that the 3/2-way valve serves as a pilot valve for a two as 2/2-way valves formed main valve having valve assembly, wherein the pilot valve, the first of the main valves for Zuseitu für of the fluid to high pressure piston-cylinder assembly in O Stammsstellurig the second main valve, which releases a connection from the piston-cylinder arrangement to a low-pressure tank, is closed, and actuates the second main valve for opening, thereby spanning the first in the closed position.
  • An advantageous embodiment of the invention may be characterized in two main valves, each having a slidably disposed within a valve body slide acted upon by the pressurized fluid control surfaces, characterized in that each main valve has three control surfaces, each of which a first and a second control surface the slider in one direction and the other third control surface act on the slider in the other direction, wherein the sum of the two equally acting control surfaces is equal to the other oppositely acting control surface.
  • control surfaces of each main valve may each correspond to a drive element, wherein the area ratio of the third control surface (third drive element) to the second control surface (second drive element) of the second main valve is always greater than the area ratio of the third control surface (third drive element) to the first control surface ( first drive element) of the first main valve.
  • control surfaces may be formed by radially extending annular surfaces and / or radially extending end faces on the slides.
  • valve arrangement or the valve system may be characterized in that the third control surface of the first main valve is formed by the end face of the slide and connected to the pilot valve.
  • first and second control surfaces of the first main valve may be formed by integrally formed on the slider annular surfaces and an end face of the slider.
  • the second control surface of the second main valve is formed in a particularly advantageous manner by an arranged on the slide of the second main valve annular surface and is connected to the pilot valve.
  • the end faces of the slide of the second main valve are in this case as a third control surface with the low-pressure tank in combination.
  • each main valve can be acted upon by the pilot valve alternately with high-pressure fluid.
  • the first control surface of the first main valve are permanently connected via a high pressure supply line with high pressure and the first control surface of the second main valve are permanently connected to low pressure.
  • valve system may be characterized in that the second control surfaces of the first and second main valve with the first main valve open and the second closed main valve with high pressure and with the first closed main valve and opened second main valve with low pressure.
  • Each main valve can each contain a helical compression spring, which acts on the associated slide in the closing direction. But they are not necessary.
  • a further embodiment of the valve system may be characterized in that the slide of the second main valve has a longitudinal bore which completely penetrates the slide, so that the space accommodating the helical spring is connected to the end face and thus to the low-pressure tank.
  • valve system may be characterized in that the spool of the first main valve has a longitudinal bore partially penetrating the spool, which connects the space for receiving the helical compression spring with a channel inside the first main valve which is connected to the piston-cylinder assembly.
  • control surfaces of each main valve may each correspond to a drive element, the area ratio of the third control surface (third drive element) to the second control surface (second drive element) of the second main valve always being greater than the area ratio of the third control surface (third drive element) to the first control surface ( first drive element) of the first main valve.
  • the area ratios of the control surfaces to the sliders of the main valves are designed so that a significantly higher pilot pressure is required to open the first main valve than to close the second main control valve.
  • the second main valve is closed by the increasing pilot pressure and then the first main valve is opened, while with decreasing pilot pressure first the first main valve closes and then opens the second main valve.
  • the desired switching behavior is achieved by driving through a single common pilot valve without the need for a separate time-offset control of the main valves.
  • the main valves can open independently. Furthermore, an independent closing takes place when the consumer no longer requires a volume flow, e.g. because a connected working piston has reached its end position.
  • the hydraulic forces on the first main valve cancel each other out as soon as the pressure directed towards the consumer is the same as that for the pressure supply.
  • the first main valve is opened again when the slide is closed, e.g. due to a compression spring is in the closed position In a corresponding manner, this also applies to the second main valve.
  • valve assembly according to the invention is shown schematically, the invention, further advantageous embodiments of the invention and other advantages will be explained and described in detail.
  • the Fig. 1 schematically shows a circuit diagram with valve assembly 10 with two main valves 11 and 12 and a pilot valve 13.
  • the two main valves 11 and 12, hereinafter referred to briefly as the first and second valves 11, 12 are 2/2-way valves with different structure, as on will be explained in more detail below.
  • the one output 14 of the first valve 11 is connected via a connecting line 21 with a piston-cylinder assembly 15 which has a piston 17 in a cylinder housing 16 on which a piston rod 18 is integrally formed.
  • the output 14 is connected to the space 19 above the piston 17.
  • the space 20 below the piston 17 is connected via a line 55 to a high pressure supply 27, which is not important for the functionality, since the restoring force of the piston 17 can also be applied differently, for. B. by a spring.
  • a further connecting line 22 is connected to a node 23, which is called with an output port 24, short opening or output 24, which is also closed here in the position shown.
  • the outlet 24 is located at the second valve 12.
  • the two valves 11 and 12 each have a further opening or outlet 25 and 26, of which the opening 25 of the valve 11 with a high pressure supply 27, which may be a high pressure accumulator or a pump, and the opening 26 of the valve 12 with a low pressure tank 28th , which is here only symbolically represented, is connected.
  • the opening 25 is connected via a return line 29 with a first drive element 30 of the valve 11 and the opening 14 via a return line 33 with a second drive element 35 of the valve 11.
  • the opening 26 is connected via a return line 31 with a first drive element 32 of the valve 12 and the opening 24 via a return line 34 with a second drive element 36 of the valve 12.
  • the two formed as 2/2-way valves valves 11 and 12, the pilot valve 13 is assigned, which is designed here as a 3/2-way valve. It has openings 37, 38 and 39.
  • the opening 38 is connected to the high pressure supply 27 and the opening 37 to the low pressure tank 28.
  • the opening 39 may be connected to either the high pressure supply 27 or the low pressure tank 28 by actuation of a solenoid control 40 and 41 or any other external force application.
  • the output port 39 is connected via a node 54 with lines 52 and 53 each having a third drive element 42 and 43 of the valves 11 and 12.
  • the third drive element 42 of the valve 11 is used to spend the valve 11 in its open position when the port 39 of the pilot valve 13 is connected to the high-pressure supply 27.
  • the third drive element 43 of the valve 12 serves to close the second valve 12 when the connection opening 39, or also briefly the connection 39, of the pilot valve 13 is connected to the high-pressure supply 27.
  • connection opening is also referred to as “connection” in the following.
  • the space 19 is connected below the piston 17 to the high pressure supply 27 and the piston 17 extends out of the cylinder housing 16.
  • the pressure also decreases at the third drive elements 42 and 43.
  • the first drive element 30 close the first valve 11 and the second drive element 36, the second valve 12 open.
  • the space 19 above the piston 17 is connected to the low-pressure tank 28, and the piston 17 moves into the cylinder housing 16.
  • control elements 30, 35, 32, 36 as well as the drive elements 42 and 43 will be described in terms of structure and operation below in connection with the Fig. 2 and 3 where the term "drive element" is explained.
  • the valve 11 has a valve body 200 surrounding an interior 201 in which a slider 202 is slidably movable.
  • the inner space 201 has a first inner space portion 203 and a second inner space portion 204, which has an inner diameter larger than that of the inner space portion 203.
  • the two interior sections 203 and 204 are connected to each other via a radial annular surface 205, which forms a step.
  • the second interior section 204 also referred to as the second section for short, is closed by a floor 206 which has a recess 207, see below.
  • region 229 which acts as a sealing surface and in this case is shown as a chamfered chamfer.
  • the valve body 200 has approximately in the middle region a bore 212 which radially passes through the valve body 200 and opens into the space 201. In the region of the section 204 of the valve body 200, a further, extending perpendicular to the longitudinal extent of the valve body 200 bore 220 opens.
  • the slider 202 is slidably mounted. It has a first slide portion 221 whose outer diameter corresponds to the inner diameter of the portion 203, a second slide portion 222, whose outer diameter is smaller than the outer diameter of the first Section 203 and dimensioned so that fluid can flow therethrough, a third slide portion 223 which is slightly larger than the inner diameter of the portion 203, so that at the sealing surface 229 can be made a seal, when the slider 202 all the way to the left (in the drawing ), and a fourth slide portion 224 whose outer diameter corresponds to the inner diameter of the recess 207 and is smaller than the outer diameter of the slide portion 221 but larger than the outer diameter of the slide portion 222.
  • the fourth slide portion 224 engages permanently in the recess 207, ie in any position of the slider 202, as well as the slide portion 221 engages permanently in the slide portion 203 a.
  • a helical compression spring 227 is disposed in a spring receiving space formed therebetween 231, with its one end against the end face 225 and with its other end is supported against the bottom 226 of the recess 207 and pushes the slider 202 to the left (in the drawing), so that the slide portion 223 is applied or pressed with its the bevel 229 facing sealing edge 228 against the acting as a sealing surface bevel 229.
  • the inner edge of the annular surface 205 is chamfered, so that the sealing edge 228 of the slider 202 against the chamfer or chamfer 229 z. B. is pressed by the force of the helical compression spring 227 and thus causes a seal.
  • the sealing edge 228 could be chamfered and come to rest at a non-angle or other beveled inner edge between the portion 203 and the annular surface 205, which could be a variant.
  • any other design of a sealing contact would be conceivable.
  • an inner bore 230 extends inside the slide 202, so that the space 235 is in the region of the second slide portion 222 with the spring receiving space 231 in which the spring 227 is in communication. If in the space 235 in the region of the second slide portion 222 high-pressure fluid, then the pressure will also be present in the spring receiving space 231 with the spring 227 and support the force of the helical compression spring 227 and the dimensions due to the dimensions Push slide 202 with the third slide portion 223 against the annular surface 205 and the chamfer 229.
  • the element referred to as the third trigger element 42 acts as a third control surface, which is formed by the free end face 232 of the slider 202.
  • the second trigger element 35 acts as a second control surface formed by the annular surfaces 233, 236 and the end surface 225 on the slider 202, which annular surfaces 233 and 236 are located between the slide portion 221 and 222 and the slide portions 222 and 223.
  • the first trigger member 30 acts as a first control surface formed by the annular surface 234 between the slider portions 223 and 224.
  • the face 232 is equal to the sum of the annular surfaces 233, 234 and the end faces 225 minus the annular surface 236, so that when the main valve 11 as well as the line 52 are under high pressure, the slider 202 exclusively by the force of the spring 227 against the sealing surface or chamfer 229 is pressed.
  • the helical compression spring 227 would not be necessary for the function and therefore could be omitted; it only supports the switching process, see below; the slider 202 would be freely movable in the valve body because the forces are all in equilibrium.
  • the pilot valve 13 is connected via the connecting line 52 with the third trigger element 42 of the first valve 11, wherein the pending in the connecting line 52 pressurized fluid acts on the free end face 232 of the slider 202.
  • first drive element 30 thus corresponds to the first control surface, the second drive element 35 of the second control surface and the third drive element 42 to the third control surface, in each case the first valve 11.
  • Fig. 3 shows a schematic longitudinal sectional view of the main valve 12.
  • This has a valve body 300, whose inner space 301 has a plurality of sections with different inner diameter; at the left in the drawing includes a first section 302, which merges into a second section 304 of slightly larger diameter with the interposition of an inner channel 317 via a conical step or chamfer opening, also referred to as chamfer 303, to the other end of the valve body 300.
  • the section 304 is followed by a bottom section 306 into which a recess 308 is inserted, whereby the valve body 300 is closed at this end.
  • Valve body 300 has two bores 315 and 316 extending transversely to its longitudinal axis, of which first bore 315 opens into inner channel 317 between first and second sections 302 and 304.
  • the second bore 316 opens into the portion of the portion 304 facing the bottom portion.
  • the first bore 315 is thus located in the region of the transition plane from the first to the second section 302, 304 of the valve body 300, wherein the inner space 317 adjoins the cone stage 303.
  • the bore 315 corresponding to the opening 24 is the conduit 22 and the second bore 316 is associated with the third driver 43.
  • a slide 314 is received, which has a first portion 318, whose outer diameter is slightly larger than the inner diameter of the first portion 302 of the valve body 300, so that the slide 314 can abut with its end or sealing edge 319 against the cone stage 303 when the slider 314 is in the in the Fig. 3 drawn position is located.
  • the outer diameter of the section 318 is to be dimensioned so that sufficient fluid can flow through when the sealing edge is open.
  • the slide 314 seals the annular space 317 against the region 321 located in front of the end face 320 adjoining the sealing edge 319 within the first section 302 of the valve body 300, to which region 321 the low-pressure tank 28 is connected.
  • the sealing contact consisting of the chamfer 303 and 319 can also be performed geometrically different, which is not important for the functionality of the system.
  • the first section 318 of the slide 314 is adjoined by a second section 322 having a larger outer diameter, whereby a step 323 facing the end face 320 is formed, onto which the pressurized fluid present in the annular space 317 forms a Force that pushes the slider 314 against the bottom surface 309 of the recess 308 of the valve body 300.
  • the second section 322 of the slide 314 is adjoined by a third section 324, with which the slide 314 engages inside the recess 308.
  • a helical compression spring 326 which acts on the slide 314 with its sealing edge 319 against the conical surface or - level 303.
  • the outer diameter of the third portion 324 is smaller than that of the first portion 318.
  • the slide 314 has a longitudinal bore extending in its longitudinal direction 327, which opens into the end faces 320 and 331 and thus into the space 325 and thus connects the spaces 321 and 325 with each other.
  • room 321 is constantly low pressure because it is connected to the low-pressure accumulator 28. Accordingly, the terminal 26 is equal to the space 321.
  • the transition between the sections 322 and 324 is formed by an annular surface 330.
  • the second control surface formed by the annular surface 323 corresponds in the circuit diagram of Fig. 1 the second drive element 36 and the third control surface formed by the annular surface 330, the third drive element 43; the first control element 32 corresponding first control surface is formed by the difference of the end faces 320 and 331.
  • valve assembly The operation of the valve assembly is as follows:
  • the pressure fluid passes via the line 52 to the third drive element 42 of the first valve 11, which corresponds to the end face 232 of the slider 202, and displaces the slider 202 against the pressure force acting on the slider 202 by the first drive element 30 of the first valve 11 , and the force of the compression spring 227 to the right (in the drawing), so that the sealing edge 228 lifts from the sealing surface 229 and the terminal 25 is connected to the terminal 14, so that high-pressure fluid to the space 19 above the piston 17 passes and the piston 17 extends out of the cylinder 16.
  • the pilot valve 13 is reversed, so that low-pressure fluid is present at the port 39, so that the force acting on the first drive element 30 from the high-pressure fluid shifts the slide 202 to the left and thus through the contact the sealing edge 228 on the sealing surface 229, the terminals 25 and 14 separates.
  • the third drive element 43 of the second valve 12 is connected via the line 53 to the low-pressure accumulator 28, so that the slide 314 by the force of the pressure in the line 22 and 34 on the second drive element 36 in the form of the annular surface 323 of the second valve 12 acts, is moved against the force of the compression spring 326 to the right, thereby connecting the terminals 24 and 26 connected.
  • the fluid can flow from the space 19 above the piston 17 via the terminals 24,26 to the low pressure accumulator 28 and the force acting on the piston 17 to the right, z. B. by the application of the space 20 with the pressure from the high pressure supply, moves the piston 17 into the cylinder 16 into it.
  • the design of the area ratios according to the invention ensures that only one main valve 11 or 12 is always closed before the respective other valve can be opened, without a time-delayed control of the two main control valves 11, 12 is necessary. In order to achieve this, it must be ensured that the area ratio of the third drive element 43 of the second valve 12 and of the second drive element 36 of the second valve 12 is always greater than the area ratio of the third drive element 42 of the first valve 11 and (for) of the first drive element 30 of the first valve 11
  • the slides have, as mentioned above, depending on a longitudinal bore, wherein the longitudinal bore 230 is connected to the slider 202 of the first main valve 11 with the space of the first main valve 11, based on the piston-cylinder assembly 15 facing surface fluidly behind the control edge, ie behind the sealing point 228/229, lies.
  • a particular advantage of the invention is that after completion of the movement of the piston 17 when using the two compression springs 326 and 227 close both main valves 11 and 12 due to the applied forces again. This allows an immediate opening of the required main valve at the next switching of the pilot valve without a loss of time by the previous closing the other main valve, if the switching takes place at a time when no volume flow is implemented at the consumer.
  • This is achieved in that the two control surfaces on one side of a main valve are each the same size as the oppositely acting individual control surface. As a result, the hydraulic forces on the main valve cancel each other as soon as the same pressure is applied to all ports.
  • valve bodies in which outer surfaces of the slide slide, can be dimensioned as a gap seal;
  • ring seals are used.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Driven Valves (AREA)
  • Multiple-Way Valves (AREA)

Claims (11)

  1. Agencement de soupapes pour l'actionnement du piston (17) d'un agencement cylindre-piston (15) pour l'actionnement de l'élément de contact mobile (50) d'un commutateur de puissance haute tension (51), comprenant une soupape à 3/2 voies (13), qui, par le biais de deux soupapes principales (11, 12) coopérant avec la soupape à 3/2 voies (13), dans une première position, commande à la fermeture la voie pour le fluide soumis à une haute pression vers l'espace (19) au-dessus du piston (17), et, dans une deuxième position, relie cet espace à un réservoir basse pression pour décharger l'espace (19) au-dessus du piston (17), caractérisé en ce que la soupape à 3/2 voies (13), sert de soupape pilote pour l'agencement de soupapes principales présentant des soupapes principales (11, 12) réalisées en tant que deux soupapes à 2/2 voies (11, 12), la soupape pilote (13) amenant dans la position d'ouverture la première des soupapes principales (11) pour la commande à la fermeture du fluide haute pression par rapport à l'agencement cylindre-piston (15), la deuxième soupape principale (13), qui libère une liaison de l'agencement cylindre-piston (15) à un réservoir basse pression (28), étant fermée, et commandant la deuxième soupape principale (12) à l'ouverture, et amenant la première soupape principale (11) dans la position de fermeture, les deux soupapes principales (11, 12) présentant à chaque fois un tiroir (202 ; 314) disposé de manière coulissante à l'intérieur d'un corps de soupape (200 ; 300) avec des surfaces de commande (232, 233, 236, 234, 225 ; 320, 323, 330, 331) pouvant être sollicitées avec du fluide sous pression, en ce que chaque soupape principale (11 ; 12) présente à chaque fois trois surfaces de commande, dont une première et une deuxième surface de commande sollicitent le tiroir (202, 314) dans une direction et dont l'autre troisième surface de commande sollicite le tiroir (202, 314) dans l'autre direction, la somme des deux surfaces de commande agissant dans le même sens étant égale à l'autre surface de commande agissant dans le sens opposé, et chaque soupape principale (11, 12) contenant un ressort respectif (227, 326) qui sollicite le tiroir associé (202, 314) dans la direction de fermeture.
  2. Agencement de soupapes selon la revendication 1, caractérisé en ce que les surfaces de commande sont formées par des surfaces annulaires s'étendant radialement et/ou par des surfaces frontales s'étendant radialement sur les tiroirs (202, 314).
  3. Agencement de soupapes selon la revendication 2, caractérisé en ce que la troisième surface de commande de la première soupape principale (11) est formée par la surface frontale (232) du tiroir et est reliée à la soupape pilote (13).
  4. Agencement de soupapes selon la revendication 2 ou 3, caractérisé en ce que les première et deuxième surfaces de commande de la première soupape principale (11) sont formées par des surfaces annulaires (233, 236, 234) façonnées sur le tiroir (202) et par une surface frontale (225) du tiroir (202).
  5. Agencement de soupapes selon l'une quelconque des revendications précédentes, caractérisé en ce que la troisième surface de commande de la deuxième soupape principale (12) est formée par une surface annulaire (330) disposée sur le tiroir (314) de la deuxième soupape principale (12) et est reliée à la soupape pilote (13).
  6. Agencement de soupapes selon l'une quelconque des revendications précédentes, caractérisé en ce que les surfaces frontales (320, 331) du tiroir (314) de la deuxième soupape principale (12), en tant que première surface de commande, sont en liaison avec le réservoir basse pression (28).
  7. Agencement de soupapes selon l'une quelconque des revendications précédentes, caractérisé en ce que la troisième surface de commande de chaque soupape principale (11, 12) peut être sollicitée par le biais de la soupape pilote (13) en alternance avec du fluide haute pression.
  8. Agencement de soupapes selon l'une quelconque des revendications précédentes, caractérisé en ce que la première surface de commande de la première soupape principale (12) est connectée de manière durable à la haute pression par le biais d'une conduite d'alimentation haute pression, et la première surface de commande de la deuxième soupape principale (12) est connectée de manière durable à la basse pression.
  9. Agencement de soupapes selon l'une quelconque des revendications précédentes, caractérisé en ce que les deuxièmes surfaces de commande de la première et de la deuxième soupape principale (11, 12), lorsque la première soupape principale (11) est ouverte et que la deuxième soupape principale (12) est fermée, sont sollicitées avec une haute pression, et lorsque la première soupape principale (11) est fermée et que la deuxième soupape principale (12) est ouverte, sont sollicitées avec une basse pression.
  10. Agencement de soupapes selon l'une quelconque des revendications précédentes, caractérisé en ce que le tiroir (314) de la deuxième soupape principale (12) présente un alésage longitudinal (327) traversant complètement le tiroir (314), de telle sorte que l'espace (325) recevant le ressort hélicoïdal (326) soit relié à la surface frontale (320) et donc au réservoir basse pression.
  11. Agencement de soupapes selon l'une quelconque des revendications précédentes, caractérisé en ce que le tiroir (202) de la première soupape principale (11) présente un alésage longitudinal (230) traversant partiellement le tiroir (202), lequel relie l'espace (231) pour recevoir le ressort de compression hélicoïdal (227) à un canal (235) à l'intérieur de la première soupape principale (11), qui est reliée à l'agencement cylindre-piston (15).
EP20100002602 2009-03-26 2010-03-12 Agencement de vannes Active EP2234135B1 (fr)

Applications Claiming Priority (1)

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DE200910014421 DE102009014421A1 (de) 2009-03-26 2009-03-26 Ventilanordnung

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Cited By (2)

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EP2933816A1 (fr) 2014-04-16 2015-10-21 ABB Technology AG Soupape hydraulique destinée à éviter les fuites dans un mécanisme de commande d'un commutateur de puissance à moyenne ou haute tension
DE102015121719A1 (de) 2015-12-14 2017-06-14 Abb Schweiz Ag Ventilanordnung zur hydraulischen Ansteuerung einer Kolben-Zylinderanordnung eines Hoch- oder Mittelspannungsleistungsschalters

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EP2638292B1 (fr) * 2012-02-09 2016-02-03 Mitsubishi Heavy Industries, Ltd. Machine à fluide de travail avec actionnement de soupape
DE102012020066A1 (de) * 2012-10-12 2014-04-17 Robert Bosch Gmbh Ventilanordnung
US9913957B2 (en) * 2012-12-05 2018-03-13 Shenzhen Mindray Bio-Medical Electronics Co. Ltd. Power switch for auxiliary common gas outlet
CN104632746B (zh) * 2015-03-04 2017-11-24 徐州重型机械有限公司 切换阀、切换液压系统以及起重机
JP6475522B2 (ja) * 2015-03-13 2019-02-27 川崎重工業株式会社 油圧システム
JP6470129B2 (ja) * 2015-06-25 2019-02-13 株式会社東芝 遮断器用油圧操作機構の監視システム及びその監視方法
JP6909743B2 (ja) * 2018-02-26 2021-07-28 株式会社東芝 蒸気弁駆動装置
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Cited By (2)

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Publication number Priority date Publication date Assignee Title
EP2933816A1 (fr) 2014-04-16 2015-10-21 ABB Technology AG Soupape hydraulique destinée à éviter les fuites dans un mécanisme de commande d'un commutateur de puissance à moyenne ou haute tension
DE102015121719A1 (de) 2015-12-14 2017-06-14 Abb Schweiz Ag Ventilanordnung zur hydraulischen Ansteuerung einer Kolben-Zylinderanordnung eines Hoch- oder Mittelspannungsleistungsschalters

Also Published As

Publication number Publication date
EP2234135A2 (fr) 2010-09-29
KR101728842B1 (ko) 2017-04-21
US8464753B2 (en) 2013-06-18
DE102009014421A1 (de) 2010-09-30
KR20100108234A (ko) 2010-10-06
US20100243927A1 (en) 2010-09-30
CN101846112B (zh) 2014-11-12
CN101846112A (zh) 2010-09-29
EP2234135A3 (fr) 2011-03-02

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