WO2006005290A1 - Soupape de commande electrohydraulique - Google Patents

Soupape de commande electrohydraulique Download PDF

Info

Publication number
WO2006005290A1
WO2006005290A1 PCT/DE2005/001125 DE2005001125W WO2006005290A1 WO 2006005290 A1 WO2006005290 A1 WO 2006005290A1 DE 2005001125 W DE2005001125 W DE 2005001125W WO 2006005290 A1 WO2006005290 A1 WO 2006005290A1
Authority
WO
WIPO (PCT)
Prior art keywords
control
piston
valve
chamber
grooves
Prior art date
Application number
PCT/DE2005/001125
Other languages
German (de)
English (en)
Inventor
Werner Kosean
Original Assignee
Carl Freudenberg Kg
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
Priority claimed from DE102004033514A external-priority patent/DE102004033514B3/de
Application filed by Carl Freudenberg Kg filed Critical Carl Freudenberg Kg
Publication of WO2006005290A1 publication Critical patent/WO2006005290A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K39/00—Devices for relieving the pressure on the sealing faces
    • F16K39/02—Devices for relieving the pressure on the sealing faces for lift valves
    • F16K39/022—Devices for relieving the pressure on the sealing faces for lift valves using balancing surfaces
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/44—Details of seats or valve members of double-seat valves
    • F16K1/443—Details of seats or valve members of double-seat valves the seats being in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/22—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution
    • F16K3/24—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members
    • F16K3/246—Combination of a sliding valve and a lift valve
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/70—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
    • F15B2211/7053—Double-acting output members

Definitions

  • the invention relates to an electro-hydraulic control valve for continuous control of a hydraulic resistance between zero and infinity, wherein an electrically controllable piston of the valve is adjustable against a control spring.
  • Valves of this type are known in many designs. In this case, two chambers are usually connected or disconnected via the valve as a function of an electrical connection. It is customary here to form arrangements with longitudinal slide valves or poppet valves. In longitudinal slide valves, a control piston is displaced in the longitudinal direction. The separation between the chambers is effected by appropriate overlaps. The switching times depend on the stroke and the overlaps. Due to the principle, these systems have leak oil, ie oil flows from the high to the low pressure side. The amount of leakage oil depends on the pressure difference and the overlap. The advantage of this system is the sensitive control of the amount of oil during the stroke by so-called fine control grooves. For seat valves is a Control piston moved in the longitudinal direction. The separation between the channels of the chambers is achieved by a metallic seal on the valve seat and an elastic seal on the piston. These valves have no leak oil. A fine control is not provided. The switching times are very short, as no overlaps need to be run over.
  • the object of the invention is to provide a generic valve for an electrically dependent fine control, which ensures a leaking oil-free training and allows different controls and can be formed and adapted for the different applications.
  • valve is designed as a seat valve and a flow between an inlet, a chamber and a drain of a controlled chamber via a valve seat by means of a piston with a valve plug is controllable, both sides of the piston are formed with the same acted upon cross-sectional area and over a connection in the piston both sides are connected to the chamber for force equalization and in the controlled chamber a control edge is arranged, which has a control ridge of the adjustable piston and having grooves for passage control.
  • this design as a seat valve, in addition to the continuous control of a hydraulic resistance between zero and infinity is additionally achieved that the valve in the closed state is leak-free.
  • this control simultaneously fulfills a second important function. It can be used as a security element to prevent the unwanted lowering of loads or other safety-critical movements of the movements controlled by this valve.
  • slide valves are usually used for the control of hydraulic linear and rotary motors, which can not be designed leak-free due to the principle and therefore make additional components necessary to solve safety-critical tasks systemically.
  • Another advantage is the very simple and cost-effective from a systemic point of view realization of a wide variety of control and regulation concepts by combining several of these valves.
  • the grooves arranged on the control bar of the piston as in triangular form, release larger or smaller passage cross-sections depending on the position of the piston position.
  • the grooves form a connection between the controlled chamber and the drain.
  • the adjusting movement of the piston is associated with a displacement sensor.
  • the chamber and the outlet of the valve each have pressure sensors.
  • the signals of the pressure sensors and / or the displacement sensor can be fed to a control unit and an electrical control for adjusting the piston can be carried out via predetermined control and regulation programs.
  • the chambers are connected to a pressure compensator.
  • valve housing and drive a receiving space for electrical control with control program is formed.
  • control valve is designed as a cartridge valve.
  • FIG. 1 An embodiment of the invention with different embodiments for arrangement is shown schematically. Show it:
  • FIG. 1 shows a .Schnittdargna a valve with a control via a proportional solenoid and a displacement sensor
  • FIG. 3 is a reduced view, as and 4 Fig. 2 in a fine control position and an open position,
  • FIG. 5 shows a circuit arrangement with a plurality of valves for pressure-dependent control of a cylinder with changing load
  • FIG. 6 shows a valve arrangement with a control via an on-off magnet
  • FIG. 8 shows a valve arrangement with a control via a proportional magnet and a displacement sensor and an associated control unit
  • FIG. 9 shows a valve arrangement as in FIG. 8 with additional pressure sensors
  • FIG. Fig. 10 shows an arrangement with an associated pressure compensator and a receiving space for an electrical control.
  • the illustrated valve with its housing 1 has an inlet 2 with a chamber 3 and a drain 4 with a controlled chamber 5.
  • the chambers 3.5 are connected via a valve seat 6 which is controllable via a piston 7 with a valve cone 24, connectable.
  • the piston 7 is acted upon by a control spring 8 and on the other hand by an actuating element 9 via an electrically controllable drive 10, such as a proportional solenoid, against the pressure of the control spring 8 adjustable.
  • an electrically controllable drive 10 such as a proportional solenoid
  • a displacement sensor is assigned to the drive 10.
  • the piston 7 is provided on both sides for force equalization with the same acted upon cross-sectional area and acted upon by a connection 11 in the piston 7 on both sides with the present pressure of the chamber 3.
  • the piston 7 is inserted in this case via elastic seals 12 in the housing 1.
  • the piston 7 is provided with a control bar 13, which corresponds in the controlled chamber 5 with a housing-side control edge 14.
  • This control bar 13 has peripheral grooves 15 as Fein Kunststoffnuten on the pressure oil can be supplied.
  • these grooves 15 are released only verstellpin, where also the Released cross-section can change depending on the height. This is achieved as in the embodiment by triangular grooves 15.
  • the chamber 3 and the drain 4 are provided in this case with corresponding pressure sensors 17, 18 to perform a pressure-independent control.
  • the displacement sensor 16 By the displacement sensor 16, the influence of the flow force is eliminated when using an associated control unit 19. In this scheme, the amount depends on the pressure difference in the chambers 3, 5.
  • FIG. 5 a basic circuit arrangement with a plurality of 2/2 directional seat valves 20 with proportional magnet 10 and displacement sensors 16 is shown, wherein control is effected via a control device 19 and corresponding pressure sensors 21 are assigned. This arrangement is used for pressure-dependent control of a cylinder 22 with changing load.
  • the seat valve 6 is opened via the piston 7 against the control spring 8 via on-off magnets 10.
  • the flow rate is dependent on the opening cut on the control bar 13 of the piston 7, thus thus the stroke of the piston 7 and the pressure drop at the control edge.
  • the two-sided coextensive and pressure balanced piston design allows oil flow in both directions. This system eliminates unwanted closing or opening forces.
  • a seal 12 seals the piston guide and the valve is leak-free due to a metallic sealing seat.
  • an on-off magnet is arranged as the drive 10 and opens the seat valve via the piston 7 against the control spring 8.
  • the seat-piston construction which is coextensive and pressure-equalized on both sides, allows the oil flow in both directions. As a result, unwanted closing or opening forces are eliminated.
  • a seal 12 seals the piston guide and through the metallic sealing seat, the valve is leak-free. By a damping nozzle 23, a switching shock can be prevented.
  • the seat valve is opened via a proportional magnet 10.
  • the current intensity and thus the stroke of the piston 7 is calculated by a control unit 20 on the basis of the specifications, wherein via a displacement sensor 17 is controlled.
  • the stroke of the piston 7 is calculated by the control unit 19.
  • the measured by the pressure sensors 17,18 upstream and downstream of the throttle flow resistance and the determined by the displacement sensor 16 position of the piston 7 is compared with a predetermined characteristic field.
  • a change in the flow resistance due to pressure or quantity changes is detected and the control unit specifies the corrected adjustment over the current to keep a flow constant.
  • the displacement sensor 16 in this case allows a very fast control speed and higher accuracy in the low flow range.
  • the two-sided coextensive and pressure balanced seat-piston construction allows the oil flow in both directions. This system eliminates unwanted closing or opening forces.
  • a receiving space 26 for an electrical control with control and computer program between the actual valve housing 1 and the drive 10 is additionally provided.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

L'invention vise à créer une soupape de commande électrohydraulique destinée à une commande continue. Cela permet de régler un piston à commande électrique de la soupape à l'encontre d'un ressort de réglage. La soupape est réalisée comme soupape à siège qui est placée entre l'admission et l'évacuation. Ainsi les deux côtés du piston sont réalisés avec une surface de coupe transversale sollicitée identique aux fins de décharge de pression et reliés à l'admission par une liaison dans le piston des deux côtés. Le siège de soupape doté d'une chambre commandée est associé à une rampe hélicoïdale qui correspond à un segment de commande du piston et présente des rainures destinées à la commande fine et réglables en fonction de la hauteur par réglage du piston.
PCT/DE2005/001125 2004-07-08 2005-06-24 Soupape de commande electrohydraulique WO2006005290A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102004033514.1 2004-07-08
DE102004033514A DE102004033514B3 (de) 2004-07-08 2004-07-08 Elektrohydraulisches Steuerventil
EP05001303.6 2005-01-22
EP05001303A EP1614947B1 (fr) 2004-07-08 2005-01-22 Vanne électro-hydraulique

Publications (1)

Publication Number Publication Date
WO2006005290A1 true WO2006005290A1 (fr) 2006-01-19

Family

ID=34972326

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2005/001125 WO2006005290A1 (fr) 2004-07-08 2005-06-24 Soupape de commande electrohydraulique

Country Status (1)

Country Link
WO (1) WO2006005290A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102493188A (zh) * 2011-12-06 2012-06-13 江苏紫荆花纺织科技股份有限公司 一种用于黄麻纱的上浆浆料
WO2017218991A1 (fr) * 2016-06-16 2017-12-21 Moog Inc. Dispositif de dosage de fluide

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4314585A (en) * 1978-08-23 1982-02-09 Hitachi, Ltd. Proportional type electromagnetic valve
DE4129774A1 (de) * 1991-09-07 1993-03-11 Hemscheidt Maschf Hermann Druckausgeglichenes schaltventil
US5271430A (en) * 1988-08-16 1993-12-21 Kabushiki Kaisha Komatsu Seisakusho Flow rate control valve device and flow force reduction structure
US5388613A (en) * 1993-01-13 1995-02-14 Dragerwerk Ag Valve with pressure compensation
US6293514B1 (en) * 1998-01-21 2001-09-25 A. Theobald Sa Flow regulation valve

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4314585A (en) * 1978-08-23 1982-02-09 Hitachi, Ltd. Proportional type electromagnetic valve
US5271430A (en) * 1988-08-16 1993-12-21 Kabushiki Kaisha Komatsu Seisakusho Flow rate control valve device and flow force reduction structure
DE4129774A1 (de) * 1991-09-07 1993-03-11 Hemscheidt Maschf Hermann Druckausgeglichenes schaltventil
US5388613A (en) * 1993-01-13 1995-02-14 Dragerwerk Ag Valve with pressure compensation
US6293514B1 (en) * 1998-01-21 2001-09-25 A. Theobald Sa Flow regulation valve

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102493188A (zh) * 2011-12-06 2012-06-13 江苏紫荆花纺织科技股份有限公司 一种用于黄麻纱的上浆浆料
WO2017218991A1 (fr) * 2016-06-16 2017-12-21 Moog Inc. Dispositif de dosage de fluide
US10203704B2 (en) 2016-06-16 2019-02-12 Moog Inc. Fluid metering valve

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