EP1369596A2 - Agencement de distributeur hydraulique - Google Patents

Agencement de distributeur hydraulique Download PDF

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Publication number
EP1369596A2
EP1369596A2 EP20030076582 EP03076582A EP1369596A2 EP 1369596 A2 EP1369596 A2 EP 1369596A2 EP 20030076582 EP20030076582 EP 20030076582 EP 03076582 A EP03076582 A EP 03076582A EP 1369596 A2 EP1369596 A2 EP 1369596A2
Authority
EP
European Patent Office
Prior art keywords
valve
tappet
pressure
connection
arrangement according
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
EP20030076582
Other languages
German (de)
English (en)
Other versions
EP1369596A3 (fr
EP1369596B1 (fr
Inventor
Martin Raadkjaer Joergensen
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.)
Danfoss Power Solutions ApS
Original Assignee
Sauer Danfoss ApS
Sauer Danfoss Nordborg ApS
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 Sauer Danfoss ApS, Sauer Danfoss Nordborg ApS filed Critical Sauer Danfoss ApS
Publication of EP1369596A2 publication Critical patent/EP1369596A2/fr
Publication of EP1369596A3 publication Critical patent/EP1369596A3/fr
Application granted granted Critical
Publication of EP1369596B1 publication Critical patent/EP1369596B1/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
    • 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
    • F15B11/003—Systems with load-holding 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
    • Y10T137/87233—Biased exhaust valve
    • Y10T137/87241—Biased closed

Definitions

  • the invention relates to a hydraulic valve arrangement with a supply connection arrangement, the one Has high pressure connection and a low pressure connection, a working connection arrangement, the two working connections has a control valve between the supply connection arrangement and the working connection arrangement is arranged, and a check valve for every working connection between the control valve and the respective work connection is arranged and its valve element mechanically using a Tappet is controllable.
  • Such a hydraulic valve arrangement is from DE 40 28 887 A1 known.
  • There the plunger opens of the respective check valve on an inclined surface on Control valve slide actuated.
  • Through the opening of the check valve is a return of the engine in one undeflected or extended condition too possible if only a small load on the motor acts, for example the dead weight, and this load is so low that it is used to open the check valve necessary pressure via any auxiliary valves can't muster.
  • a hydraulic valve arrangement with check valves is mainly for mounting on tractors or others Machines thought.
  • the check valves should ensure that the behavior is as leakproof as possible, i.e. they are to be connected to the working connection arrangement Hold the motor in a certain position, if this is set by the control valve.
  • the Check valves are opened with the help of a pilot pressure. This is for example from DE 199 31 142 A1 or 199 19 015 A1. However, this requires that the engine has sufficient pilot pressure can generate.
  • valve arrangement must therefore be able both for double-acting motors and for single-acting motors to open the check valves. If, for example, the field rail on a tractor is controlled via the valve arrangement on the Field rail but no weight rests, then there is hardly any a load to lower the farm rail. The pressure in the tank line should be almost 0 bar, which in is usually relatively difficult to implement.
  • DE 40 28 887 A1 therefore has a positive opening of the Check valves provided. If the spool of the control valve is moved in one direction, then it poses on the one hand the necessary hydraulic connections to operate the motor in one direction. At the same time, the check valve is over the plunger and opened the slide to drain the liquid from the opposite pressure chamber of the engine enable.
  • the invention has for its object when in use of a single-acting motor that of supply reliably open the check valve can.
  • the pressure chamber of the plunger for a check valve is limited by the valve element of the other check valve.
  • the slide of the control valve or a corresponding valve element
  • the valve arrangement with a motor to operate, which is arranged on both work ports or with an engine running on only one Work connection is arranged and accordingly one-sided acts.
  • the free work connection must be with this Design can only be closed. If now with the help of the control valve the pressure to itself closed work connection, then there the check valve turned open. The pestle will moved accordingly to the check valve on the other Tax on the work connection.
  • the opening of the check valve at the closed work connection is not critical, because the hydraulic fluid does not escape anyway can, regardless of whether the check valve is open is or not.
  • a common plunger is provided for both check valves.
  • the plunger can then do one or the other Open the shut-off valve when the pressure on the other Check valve is present.
  • the use of a single Tappet simplifies the construction. You have beyond that the advantage that the one-way motor in Connect basically to each of the two working connections can without the function of the valve assembly is adversely affected.
  • the plunger is preferably shorter than the distance between the valve elements of the two check valves. In an operating mode in which both work connections with connected to the motor, the plunger does not interfere. It may be so charged that it is a Check valve opens when the other check valve goes through the pressure at the high pressure connection is opened, which is caused by the control valve is directed there. In this case is the opening of the other check valve anyway required. If the ram is shorter than the distance between the valve elements of the two check valves, there is definitely a position in which he both check valves not acted on.
  • the valve element and / or the At least on their common contact surface a shape on that the penetration of liquid allowed between the plunger and the valve element.
  • the plunger can, moreover, be relative be thin.
  • the force acting on the plunger only has to sufficient to overcome a force that, for example from a closing spring to the valve element of the check valve is exercised.
  • Such Forming can for example be a groove that in the surface of the valve element of the check valve is arranged is. It can also have a projection on the front of the pestle. Other configurations are conceivable and easily findable for the expert.
  • the tappet and the valve elements of the two check valves preferably have a common axis of movement.
  • the tappet and the two valve elements thus move along a straight line. This keeps wear down.
  • the ram is only loaded along its direction of movement.
  • the guidance of the tappet in the housing is therefore not burdened by laterally acting forces.
  • the pressure chamber can preferably be connected to a leakage oil discharge device.
  • the tappet will have no influence on the valve function.
  • the leakage oil discharge device is provided, via which a correspondingly excessive amount of hydraulic fluid can be discharged before the pressure becomes too great.
  • the leak oil discharge device ensures that a leak cannot lead to pressure build-up at the work connections.
  • the leak oil discharge device has an orifice that connects to the low pressure connection forms.
  • the cover prevents that if there is a desired increase in pressure in the corresponding Too much hydraulic fluid is draining from the pressure chamber can.
  • the panel is preferably in a load sensing line arranged in the neutral position of the control valve is connected to the low pressure connection. This is a relatively simple design.
  • the load sensing line is connected to the work connections anyway. This is required to be the highest in the system occurring pressure to the pump or an associated Report control device. You can now do this Give the load sensor line a second function. she serves namely, smaller amounts of leakage of hydraulic fluid dissipate.
  • the valve element is preferably both mechanical can be controlled hydraulically with the tappet.
  • the Hydraulic valve opening is typical at high pressures, for example 10 bar to 400 bar, and large flow rates, whereas the mechanical solution at lower pressures, e.g. between 0 and 10 bar and small flow rates used becomes.
  • a hydraulic valve arrangement 1 has a housing 2 on.
  • Two working connections A, B are provided in the housing 2, which together form a working connection arrangement form.
  • a control valve 3 is arranged, which has a slide 4, only shown schematically, the in a bore 5 in the housing 2 under the Effect of a drive 6 is displaceable.
  • the hole 5 has a series of circumferential grooves 7-13.
  • the Slider 4 has a series of circumferential grooves 14-19. By moving the slide 4, the Position circumferential grooves 14-19 so that certain neighboring ones Circumferential grooves 7-13 in the bore 5 with each other get connected.
  • the representation of the slide 4 with its grooves 14-19 is therefore not to scale. But since the formation of such a control valve 3rd known with a slider 4 in a bore a detailed explanation is dispensed with.
  • the circumferential groove 7 is connected to the outlet via a channel 20 a compensation valve 21 in connection.
  • the Input of the compensation valve 21 is with the high pressure connection P connected.
  • the compensation valve 21, also known as a pressure compensator or pressure regulator ensures that the control valve 3 there is always the same pressure drop.
  • the control valve 3 is on a first working line 22 with the working connection A in connection and via a second working line 23 with the working connection B.
  • a first check valve 24 arranged, which has a valve element 25, that by a compression spring 26 in contact with one Valve seat 27 is held.
  • the check valve 24 is controllable by a pressure in the working line 22 prevails. The prerequisite for this is that the Pressure in the working line 22 is so great that it Force of the compression spring 26 overcomes.
  • valve element 29th has, by a compression spring 30 against a valve seat 31 is pressed.
  • the valve element 29 can from Valve seat 31 can be lifted when the pressure in the second working line 23 is large enough.
  • the pressure in the two working lines 22, 23 is by the Slider 4 of the control valve 3 controlled.
  • the other work port B is closed. This is symbolized by a check valve 35.
  • a plunger 36 arranged in a bore 37 is displaceable in the housing.
  • the axis of the hole and thus also the axis of the plunger 36 is correct coincides with the axis 48 of the valve elements 25, 29 of the Check valves 24, 28.
  • the working line 22 has one in front of the check valve 24 first pressure chamber 38.
  • the pressure in the first pressure room 38 controls the opening movement of the valve element 25 of the first check valve 24.
  • the pressure in the pressure chamber 39 controls the opening movement of the valve element 29 of the second Check valve 28.
  • the plunger 36 now ends in the two pressure chambers 38, 39.
  • the plunger 36 is pressed by the pressure in the two Pressurized spaces 38, 39. If the pressure in the second pressure chamber 39 is greater than the pressure in the first Pressure chamber 38, then the plunger 36 in the direction of the valve element 25 of the first check valve 24 shifted. If the pressure in the second pressure chamber 39 is sufficient, to generate a force greater than the force exerted by the compression spring 26 on the valve element 25 of the first check valve 24, then the Tappet 36 is able to remove valve element 25 from the valve seat 27 take off and a connection accordingly from the work connection A to the first work line 22 release.
  • the slide 4 of the control valve 3 is moved that the channel 20 is connected by the compensation valve 21 becomes 23 with the second management a pressure builds up in the second pressure chamber 39, the plunger 36 in the direction of the valve element 25 of the first check valve 24 moves in the drawing So to the left, and the valve element 25 from the valve seat 27 stands out against the force of the compression spring 26.
  • the slide 4 has a connection between the first working line 22 and not closer Low pressure connection shown, for example can be connected to the two grooves 10, 11, so that the hydraulic fluid from the pressure chamber 33 of the motor 32 can flow off.
  • the plunger 36 is in the rest position shown on the valve element 29 of the second shutoff valve 28.
  • a formation 40 in the present case Fall a groove in its surface.
  • This formation 40 doesn't have to be big. It only has to suffice to to exert sufficient pressure on the plunger 36 to lift the plunger 36 from the valve element 29. After that the entire end face of the plunger 36 stands for one Pressurization available.
  • the length of the plunger 36 is shorter than the distance between the two valve elements 25, 29. In the rest position it is entirely possible and also envisaged that the two check valves 24, 28 are closed are.
  • connection arrangement for example a double-acting motor on the two working connections A, B is connected, then the Tappet 36 capable of blocking valve 24, 28, respectively to open, in the pressure chamber 38, 39 not enough There is pressure to open it.
  • the Tappet 36 capable of blocking valve 24, 28, respectively to open, in the pressure chamber 38, 39 not enough
  • the Tappet 36 capable of blocking valve 24, 28, respectively to open, in the pressure chamber 38, 39 not enough
  • the Working port A should be pressurized, then there is a corresponding pressure in the first work management 22 under the control of the slide 4 of the Control valve 3 on. This pressure is able to do that Open check valve 24.
  • the plunger 36 moved to the right and opens the second shut-off valve 28, so that liquid from the working connection B can flow off via the working line 23.
  • valve arrangement 1 is therefore without further conversion measures both usable if one-way Motor is connected as well, if one double-acting motor is connected.
  • the plunger 36 In normal operation, the plunger 36 has no influence have the valve function. However, to completely oppose it to ensure that there is no pressure inadvertently the work lines 22, 23 or the work connections A, B can build that open the check valves 24, 28 the working connections A, B are via lines 41, 42 connected to a load-sensing connection LS. Indeed is an aperture 43, 44 for in this connection each working port A, B provided. About these panels 43, 44 may be a leakage fluid in the Neutral position of the slide 4 in the housing 2 in a or both of the working lines 22, 23 arrive. The LS line is in the neutral position of the Slider 4 connected to the low pressure connection.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Multiple-Way Valves (AREA)
EP20030076582 2002-06-05 2003-05-26 Agencement de distributeur hydraulique Expired - Lifetime EP1369596B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10224827 2002-06-05
DE2002124827 DE10224827A1 (de) 2002-06-05 2002-06-05 Hydraulische Ventilanordnung

Publications (3)

Publication Number Publication Date
EP1369596A2 true EP1369596A2 (fr) 2003-12-10
EP1369596A3 EP1369596A3 (fr) 2005-06-01
EP1369596B1 EP1369596B1 (fr) 2007-01-24

Family

ID=29432638

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20030076582 Expired - Lifetime EP1369596B1 (fr) 2002-06-05 2003-05-26 Agencement de distributeur hydraulique

Country Status (4)

Country Link
US (1) US7028710B2 (fr)
EP (1) EP1369596B1 (fr)
AT (1) ATE352720T1 (fr)
DE (2) DE10224827A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008015752A1 (fr) * 2006-08-03 2008-02-07 Shimadzu Corporation Soupape de régulation de fluide
DE102007032415B3 (de) * 2007-07-12 2009-04-02 Sauer-Danfoss Aps Hydraulische Ventilanordnung
EP2891806A1 (fr) * 2014-01-03 2015-07-08 Danfoss Power Solutions Aps Soupape hydraulique
US10590962B2 (en) * 2016-05-16 2020-03-17 Parker-Hannifin Corporation Directional control valve

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4028887A1 (de) 1990-09-12 1992-03-19 Bosch Gmbh Robert Hydraulische steuereinrichtung
DE19919015A1 (de) 1999-04-27 2001-01-18 Danfoss Fluid Power As Nordbor Hydraulische Ventilanordnung mit Verriegelungs- und Schwimmfunktion
DE19931142A1 (de) 1999-07-06 2001-01-25 Sauer Danfoss Nordborg As Nord Hydraulische Ventilanordnung mit Verriegelungsfunktion

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3125120A (en) * 1964-03-17 hasbany
US1955154A (en) * 1932-11-08 1934-04-17 Cash A W Co Valve mechanism
US2483312A (en) * 1944-08-02 1949-09-27 Bendix Aviat Corp Valve
US2959190A (en) * 1957-02-25 1960-11-08 Bendix Corp Control valve having operating position hold
US3272085A (en) * 1963-11-19 1966-09-13 Parker Hannifin Corp Fluid system and valve assembly therefor
US3818936A (en) * 1972-06-15 1974-06-25 Monarch Road Machinery Co Hydraulic control valve
US3795178A (en) * 1972-09-11 1974-03-05 R Roche Hydraulic actuator holding system
US3974742A (en) * 1974-10-31 1976-08-17 Caterpillar Tractor Co. Lock valve assembly
DE2801689C2 (de) * 1978-01-16 1982-11-11 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 8000 München Steuerventileinrichtung
DE2929232A1 (de) * 1979-07-19 1981-02-05 Bosch Gmbh Robert Steuergeraet fuer ein hydraulisch angetriebenes arbeitsgeraet
US4286432A (en) * 1979-08-30 1981-09-01 Caterpillar Tractor Co. Lock valve with variable length piston and hydraulic system for a work implement using the same
DE3322018A1 (de) * 1983-06-18 1984-12-20 Robert Bosch Gmbh, 7000 Stuttgart Hydraulisches wegeventil mit einem gehaeuse
US4518004A (en) * 1983-11-21 1985-05-21 Hr Textron Inc. Multifunction valve
DE3431104A1 (de) * 1984-08-24 1986-03-06 Robert Bosch Gmbh, 7000 Stuttgart Hydraulische steuereinrichtung
DE3441946A1 (de) * 1984-11-16 1986-05-28 Robert Bosch Gmbh, 7000 Stuttgart Hydraulische steuereinrichtung
DE4436548C2 (de) * 1994-10-13 2000-12-21 Mannesmann Rexroth Ag Ventilanordnung zur Betätigung eines hydraulischen Verbrauchers
EP1018292B8 (fr) * 1999-01-09 2005-06-29 GKN Walterscheid GmbH Dispositif de levage pour bras inférieurs d'accouplement de tracteur
US6581639B2 (en) * 2000-10-20 2003-06-24 Case Corporation Low leak boom control check valve

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4028887A1 (de) 1990-09-12 1992-03-19 Bosch Gmbh Robert Hydraulische steuereinrichtung
DE19919015A1 (de) 1999-04-27 2001-01-18 Danfoss Fluid Power As Nordbor Hydraulische Ventilanordnung mit Verriegelungs- und Schwimmfunktion
DE19931142A1 (de) 1999-07-06 2001-01-25 Sauer Danfoss Nordborg As Nord Hydraulische Ventilanordnung mit Verriegelungsfunktion

Also Published As

Publication number Publication date
ATE352720T1 (de) 2007-02-15
EP1369596A3 (fr) 2005-06-01
DE10224827A1 (de) 2004-01-08
US20030226597A1 (en) 2003-12-11
EP1369596B1 (fr) 2007-01-24
DE50306350D1 (de) 2007-03-15
US7028710B2 (en) 2006-04-18

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