EP1063431A1 - Soupape à maintien de charge - Google Patents

Soupape à maintien de charge Download PDF

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Publication number
EP1063431A1
EP1063431A1 EP00106242A EP00106242A EP1063431A1 EP 1063431 A1 EP1063431 A1 EP 1063431A1 EP 00106242 A EP00106242 A EP 00106242A EP 00106242 A EP00106242 A EP 00106242A EP 1063431 A1 EP1063431 A1 EP 1063431A1
Authority
EP
European Patent Office
Prior art keywords
valve
load
closing element
seat
shock
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.)
Granted
Application number
EP00106242A
Other languages
German (de)
English (en)
Other versions
EP1063431B1 (fr
Inventor
Martin Dipl-Ing Heusser
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.)
Hawe Hydraulik GmbH and Co KG
Original Assignee
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co 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
Application filed by Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG filed Critical Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Publication of EP1063431A1 publication Critical patent/EP1063431A1/fr
Application granted granted Critical
Publication of EP1063431B1 publication Critical patent/EP1063431B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices

Definitions

  • the invention relates to a hydraulic load holding valve in the preamble of the claim 1 specified Art.
  • the main closing element is integrally connected to the control piston in order to manage with few parts, and to be able to control a stroke-dependent quantity control function (ramp function), in which the response movements delay the control piston due to friction assisted.
  • a shock valve function is desirable in order to Pressure surge on the side of the pressure to be held for the system by an open movement to send or to dampen.
  • there are undesirably high shock function pressure values for example at a working pressure of around 200 bar at top values of around 350 bar.
  • Load control valves previously used according to DE-A-255 99 29 have an acceptable one Shock function, because the main closing element is structurally connected to the control piston is separated and these two components only cooperate via a sealed plunger. However, this results in a multi-part and expensive construction. Furthermore, do not control quantity control via the opening stroke of the main closing element, because the main closing element only from the pressure and the fluid dynamic Forces against the control spring is adjusted and thereby quickly releases the valve seat.
  • the invention has for its object a hydraulic load holding valve with flow control function to create that is structurally simple, and despite the quantity control function a fast responding shock function for moderate shock function pressure peaks he brings.
  • the separate shock valve bypasses the valve seat and not with the pilot piston connected, it responds so quickly that in the event of a shock a working pressure of approx. 200 bar, for example, only a moderate pressure peak of 240 bar arises.
  • the advantage of the simple construction of the with the control piston connected main locking element is retained. As a result of this design can be a stroke-dependent during the opening movement of the main closing element Control the quantity control in which the pilot piston thanks to its escapement helps without delaying the shock function.
  • the shock valve or its closing element expediently simultaneously forms the spring force receiving body, to avoid lateral forces on the main locking element and on the shock valve closing element is important.
  • the shock valve is a check valve in a valve seat for that Main closing element bypass channel.
  • the main closing element needs the channel, e.g. a simple axial bore.
  • the closing element of the shock valve is also the spring force receiving body. In this way, compared to the known load holding valve mentioned at the beginning only very minor modifications of the proven and cost-effective construction principle required.
  • the closing element of the shock valve can be a simple ball while the seat of the shock valve directly from the mouth of the axial bore in the main closing element is formed.
  • the quantity control channel in a proven way shaped in the stem with the valve seat for the main closing element interacts in a quantity-regulating manner, e.g. if which is for the load holding function important leak-free seating surface of the main closing element from the valve seat is lifted off.
  • the diameter of the stem and thus the diameter of the valve seat should expediently be larger than the diameter of the control piston.
  • the difference area becomes an opening force component for the main closing element derived, which supports the control piston.
  • valve seat separates the first and second chambers between them the seat pressed onto the valve seat creates freedom from leakage.
  • the circular washer is expediently guided on the shaft.
  • the quantity control channel at least one control slot machined into the shaft from the outside be one in the course depending on the opening stroke of the main closing element releases precisely predeterminable cross-section and regulates the quantity.
  • Another One possibility is to provide a cavity in the shaft to which the lead first chamber inlet openings, and at which below the seat of the Main closing element work together with the valve seat.
  • the Exhaust openings should have opening sizes that vary depending on the stroke Exactly how the flow cross-section is released depending on the stroke can predict.
  • the cavity is particularly useful at the same time the channel of the shock valve, the structural conditions that are provided anyway used in the main closing element for the shock function, namely the cavity and the inlets leading from the first chamber to the cavity.
  • valve seat and the main closing element or the control piston are expedient made of steel to small dimensions for long service life and high pressures to enable the load holding valve.
  • shock occurs when the one picked up by the load holding valve Load pressure is subjected to pressure increases due to external influences that it to dismantle or dampen quickly.
  • the shock valve opens when the pressure increases uncontrolled, i.e. pressure dependent, and can reduce the pressure increase or dampen, whereby however the load holding valve is not removed by means of the control piston the shut-off position is adjusted.
  • This shock function is a desirable safety aspect for load holding valves and assumes that the shock valve through the load pressure to be maintained is loaded in the opening direction, as is also the case if necessary the load holding valve itself.
  • a consumer V e.g. a hydraulic cylinder
  • a working line 1 adjustable against a load F The working line 1 has two line sections 1a and 1b, between which a load holding valve L is arranged.
  • a load holding valve L To adjust the Consumer V against the load F is the load holding valve L by a spring 17 loaded check valve R in a line loop 1c in the flow direction from the directional control valve W to the consumer V. It becomes the check valve R structurally integrated in the load holding valve L or arranged separately from it.
  • a main closing element H by a preferably adjustable Spring 3 is applied in the direction of the shut-off position shown.
  • a hydraulic one Control 4 is provided via a control line 5 with a variable control pressure is acted upon.
  • a pilot line 2 from the line section 1b branches off the main closing element is furthermore subjected to the load pressure in the opening direction acted upon from the shut-off position.
  • the control pressure in the control line 5 is generated and changed in a selectable manner.
  • the consumer V in FIG. 1 a hydraulic cylinder which can be acted upon on one side
  • the control pressure in one Control line 5 derived from the other working line, not shown in FIG. 1 be there to move the consumer V, for example under the load, on the Piston rod side of the piston pressure must be built up from which this Control pressure is derived.
  • the symbolic double lines of the load holding valve L indicate that this Load holding valve L has a flow control function. This means that when you open the Load holding valve from the shut-off position and a ramp function when closing the amount of pressure medium can be controlled, which is dependent on the stroke of the main closing element H. Furthermore, a shock valve S is contained in the load holding valve L.
  • the check valve R locks and locks that too Load holding valve L in the outflow direction. Both valves L, R can be designed as seat valves and are leak-free in their shut-off positions. The load F is held.
  • control line 5 which is the Main closing element H from the shut-off position shown regulating the quantity into one Adjusted the open position, namely against the force of the spring 3, so that the pressure medium from line section 1b via load holding valve L, line section 1a and the directional control valve W can flow out.
  • the speed of movement the load F depends on the level of the control pressure or the setting of the spring 3.
  • the load pressure in line section 1b supports via pilot line 2 the control function in the load holding valve. Thanks to the control function, a ramp function can be used control, i.e. the load F starts its lowering movement smoothly and holds, as soon as the pressure in the control line 5 is reduced again, without jerks.
  • the shock valve S responds to avoid critical pressure peaks for the system or reduce or dampen the shock.
  • the response of the shock valve S can take place without control pressure in the control line 5 because the shock valve S responds to the pressure difference between the line sections 1 a and 1 b.
  • the load holding valve L is arranged in a housing 6, for example the housing of the consumer, not shown in Fig. 2 may be.
  • the main closing element H consists of a head part 8, which has a conical seat 9 and thereupon has an essentially cylindrical shaft 10 which is in a Control piston 12 with a slightly smaller diameter than the shaft 10 ends.
  • a seal 13 is provided on the control piston 12, one with the control line 5 connected control chamber 7 of a first, with the line section 1b connected chamber K1 separates.
  • a disc-shaped insert e.g.
  • the Check valve R blocks in the flow direction from the first chamber K1 in the second chamber K2.
  • the flow control function of the load holding valve L is carried out by at least one flow control channel M controlled, the control slot formed in the shaft 10 in FIG. 2 11 is formed (expediently several such control slots 11 around the Circumference of the shaft) and from the first chamber K1 to just below the seat 9 extends.
  • the axial bore of the shock valve forming channel 24 S communicates with the control slot 11, so that when the Shock valve S without simultaneous opening movement of the main closing element H the closing member 22 lifts off the seat 23 and pressure medium flows out into the second chamber K2 leaves.
  • Thanks to the difference in diameter between the control piston 12 and the stem 10 or the valve seat 20 is from the pressure in the first chamber K1 also an opening force component at the main closing element H in the event of a load pressure shock effective.
  • the control piston 12 is formed in one piece dampens the opening movement, the main closing element H speaks to this load pressure shock only delayed or not for a short duration of the shock.
  • shock valve S bypassing the valve seat 20, for example, at limit a load pressure shock to around 240 bar at a load pressure of around 200 bar, because the shock valve S responds much faster than the load holding valve L.
  • the quantity control channel M is structurally different designed.
  • a cavity 27 is provided, to which over lead the circumference distributed inlets 26 (from the first chamber K1).
  • Below the Seat 9 is formed a plurality of outlets 25 from the cavity 27, which for the Flow control function are needed.
  • the channel 24 of the shock valve is axial Blind bore formed which defines the cavity 27. This has manufacturing technology Benefits.
  • The, conveniently with a slide or slide fit, in the Guide bore 19 guided, shaft 10 is in different axial distances from the seat 9 is formed with outlets 25 of different sizes. The closer to The outlets 25 lying on the seat surface 9 have smaller cross sections than the wider ones lying down. This means that depending on the opening stroke of the main closing element control a clean ramp function.
  • the closing member 22 of the shock valve S cooperates with the mouth of the channel 24 or the axial bore, the forms the seat 23 of the shock valve S.
  • the quantity control function could also be brought about by the shaft subsequently to the seat 9 a conical or with a predetermined profile gradually constricted contour.
  • the channel 24 of the Shock valve can be connected to the first chamber K1 in another way.
  • the main closing element H and the disc body 8 expediently exist made of steel and are preferably hardened and in the cooperating areas ground.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Check Valves (AREA)
EP00106242A 1999-06-24 2000-03-22 Soupape à maintien de charge Expired - Lifetime EP1063431B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE29911076U DE29911076U1 (de) 1999-06-24 1999-06-24 Hydraulisches Lasthalteventil
DE29911076U 1999-06-24

Publications (2)

Publication Number Publication Date
EP1063431A1 true EP1063431A1 (fr) 2000-12-27
EP1063431B1 EP1063431B1 (fr) 2004-06-02

Family

ID=8075271

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00106242A Expired - Lifetime EP1063431B1 (fr) 1999-06-24 2000-03-22 Soupape à maintien de charge

Country Status (2)

Country Link
EP (1) EP1063431B1 (fr)
DE (2) DE29911076U1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019218401B3 (de) * 2019-11-27 2021-04-01 Hawe Hydraulik Se Lasthalteventil, Lasthaltventilset und Verfahren zur Montage eines Lasthalteventils
DE102022207208A1 (de) 2022-07-14 2024-01-25 Hawe Hydraulik Se Hydraulikventil

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2559029A1 (de) 1975-12-29 1977-07-07 Heilmeier & Weinlein Bremsventil
GB2205385A (en) 1987-05-15 1988-12-07 Oil Control Spa Improvements in a load holding and control valve, in particular for hydraulic circuits with either open or closed centre directional control valve
DE19608801A1 (de) 1996-03-07 1997-09-18 Oil Control Gmbh Hydraulisches Lasthalte- bzw. Senkbremsventil
EP0816691A2 (fr) * 1996-07-06 1998-01-07 Robert Bosch Gmbh Vanne d'arrêt avec limitation de pression
DE29721244U1 (de) 1997-12-01 1998-05-07 Alpha Fluid Hydrauliksysteme M Steuerventil
EP0902194A1 (fr) 1997-09-15 1999-03-17 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Soupape à maintien de charge

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2559029A1 (de) 1975-12-29 1977-07-07 Heilmeier & Weinlein Bremsventil
GB2205385A (en) 1987-05-15 1988-12-07 Oil Control Spa Improvements in a load holding and control valve, in particular for hydraulic circuits with either open or closed centre directional control valve
DE19608801A1 (de) 1996-03-07 1997-09-18 Oil Control Gmbh Hydraulisches Lasthalte- bzw. Senkbremsventil
EP0816691A2 (fr) * 1996-07-06 1998-01-07 Robert Bosch Gmbh Vanne d'arrêt avec limitation de pression
EP0902194A1 (fr) 1997-09-15 1999-03-17 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Soupape à maintien de charge
DE29721244U1 (de) 1997-12-01 1998-05-07 Alpha Fluid Hydrauliksysteme M Steuerventil

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019218401B3 (de) * 2019-11-27 2021-04-01 Hawe Hydraulik Se Lasthalteventil, Lasthaltventilset und Verfahren zur Montage eines Lasthalteventils
DE102022207208A1 (de) 2022-07-14 2024-01-25 Hawe Hydraulik Se Hydraulikventil

Also Published As

Publication number Publication date
EP1063431B1 (fr) 2004-06-02
DE50006661D1 (de) 2004-07-08
DE29911076U1 (de) 1999-09-23

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