EP1381779B1 - Tiroir a balance manometrique situee a l'interieur - Google Patents

Tiroir a balance manometrique situee a l'interieur Download PDF

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Publication number
EP1381779B1
EP1381779B1 EP02727817A EP02727817A EP1381779B1 EP 1381779 B1 EP1381779 B1 EP 1381779B1 EP 02727817 A EP02727817 A EP 02727817A EP 02727817 A EP02727817 A EP 02727817A EP 1381779 B1 EP1381779 B1 EP 1381779B1
Authority
EP
European Patent Office
Prior art keywords
piston
control valve
pressure
directional control
pressure regulator
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.)
Expired - Lifetime
Application number
EP02727817A
Other languages
German (de)
English (en)
Other versions
EP1381779A1 (fr
Inventor
Winfried RÜB
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.)
Bucher Hydraulics GmbH
Original Assignee
Bucher Hydraulics GmbH
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 Bucher Hydraulics GmbH filed Critical Bucher Hydraulics GmbH
Publication of EP1381779A1 publication Critical patent/EP1381779A1/fr
Application granted granted Critical
Publication of EP1381779B1 publication Critical patent/EP1381779B1/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
    • F15B13/02—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
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F15B13/0418—Load sensing elements sliding within a hollow main valve spool
    • 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
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86694—Piston valve
    • Y10T137/86702—With internal flow passage
    • 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

Definitions

  • the invention relates to a directional valve with internal pressure compensator according to the preamble of claim 1.
  • Such valves are advantageously used in mobile hydraulics for controlling hydraulic consumers in agricultural and construction vehicles.
  • a directional control valve referred to in the preamble of claim 1 is known from DE-A1-198 55 187.
  • the directional valve has an internal pressure compensator, which is designed as a hollow slide. This has a radial opening, which is permanently connected to a radial opening of the valve piston.
  • the valve has a load-sensing annular channel which is permanently connected to a spring chamber of the pressure compensator.
  • a similar directional control valve is also known from DE-A1-198 36 564. Again, a pressure compensator is disposed within the designed as a hollow piston spool. In order to solve the existing problem of the effect of flow forces on the behavior of the directional control valve, it is proposed here to provide a second control edge on the pressure compensating piston, with which an additional flow of pressure medium to the working connection can be generated. This compensating flow is intended to minimize the flow forces on the pressure compensating piston and on the spool. This should in particular the response of the directional control valve, such as when initiating lifting and lowering operations in power lifts, be improved.
  • the realization of an additional control edge means a fabrikatorischen extra effort.
  • the compensation of flow forces is also imperfect whenever the flows are different in size.
  • the hydraulic consumer is a differential cylinder
  • the flow rate of the hydraulic medium at the two working ports A and B of the directional control valve is different.
  • such differential cylinders may have different ratios of the flow rates in the inlet and outlet.
  • the invention has for its object to provide a directional control valve, the pressure compensator is insensitive to different flow rates caused by different flow forces and at the same time ensures that it can not come in the "neutral" position to a movement of the hydraulic consumer.
  • the reference numeral 1 shows a part of a valve housing which has a longitudinal bore 2.
  • a horizontal axis of symmetry S w and a vertical axis of symmetry S s is indicated that the valve housing 1 and also a displaceable in the longitudinal bore 2 way valve piston 3 are constructed biaxial symmetrical.
  • the directional valve piston 3 is a hollow slide.
  • different ring channels are pierced by the longitudinal bore 2 ago, namely in the center of symmetry a tank connection ring channel T, the other of the vertical axis of symmetry S s in the direction of the front side of the valve housing 1 more ring channels follow, namely to the left a working connection ring channel A and to the right, a working port annular channel B.
  • These two working port ring channels A, B are in communication with the load ports of the directional control valve, commonly referred to as "A" and "B".
  • the directional control valve piston 3 in turn has an axial bore 4, in which a pressure compensating piston 5 is axially displaceable against a pressure compensating spring 6.
  • FIG. 1 shows the directional control valve piston 3 in the neutral position, in which there is no connection to the tank connection ring channel T or to the pump pressure annular channel P of the working connection ring channels A and B.
  • the pressure balance piston 5 is also a hollow slide, so enclosing an interior 7, which is open against the vertical axis of symmetry S s , but on the other side has a closed end wall 8.
  • the directional control valve piston 3 is also closed at the front, for example by means of a screw-cap 9. Between the cap 9 of the directional control valve piston 3 and the end wall 8 of the pressure compensating piston 5, the already mentioned pressure compensating spring 6 is arranged.
  • control ribs 10 These form extensions of the cylindrical part of the pressure balance piston 5.
  • a section line II-II is shown, wherein the corresponding section in FIG. 2 is shown. 2
  • the control ribs 10 are cut, while the intermediate end faces of the pressure compensating piston 5 are shown in plan view.
  • the annular portion-shaped spaces between the control ribs 10 are referred to as fine control notches and are provided with the reference numeral 11.
  • FIG. 1 For the function of the directional control valve essential elements are also shown in FIG. 1.
  • Reference numeral 19 designates a control spring which acts on the directional valve piston 3 from a drive, not shown.
  • Functional are Tank Kunststoffnuten 20 which are milled into the lateral surface of the directional control valve piston 3 and serve to allow for a corresponding relative position of the directional control valve piston 3 to the valve housing 1, the flow of the hydraulic medium from the working port-ring channel B or working port-ring channel A to the tank port-ring channel T. , which characterizes the two working positions of the directional control valve. If, for example, the directional valve piston 3 is displaced to the right from the position shown in FIG arises via the Tank Kunststoffnuten 20, the connection between the working port ring channel B and the tank port ring channel T.
  • first valve piston radial opening 21 and a second valve piston radial opening 22 whose functional importance will be discussed.
  • second valve piston radial opening 22 whose functional importance will be discussed.
  • pressure compensator spring chamber 24 a permanent connection between the load-sensing ring channel LS and the pressure compensating spring 6 surrounding space, which is referred to as pressure compensator spring chamber 24, is made.
  • the inner diameter of the directional control valve piston 3 in the region of the pressure compensator spring chamber 24 is greater than the outer diameter of the pressure compensating piston 5.
  • other means, such as longitudinal grooves, may be present.
  • the pressure compensator spring chamber 24 is functionally a control pressure chamber.
  • Essential to the invention is that between the load-sensing ring channel LS and the pressure compensator spring chamber 24 is no control edge, which could affect the pressure in the pressure compensator spring chamber 24 in an unfavorable manner.
  • the circumferential line of the pressure compensating piston 5 acts in the region of the fine control notches 10. This control edge is provided in FIGS. 1 and 2 with the reference numeral 30.
  • Essential to the invention is a well-known from the prior art feature, namely, that the pressure balance piston 5 has at least one radial opening 31 in its cylindrical shell.
  • a plurality of such radial openings 31 are present, which are distributed uniformly over the circumference of the pressure compensating piston 5.
  • Each of the radial openings 31 has the shape of an elongated slot.
  • a diameter d Dw is shown, which designates the outer diameter of the pressure compensating piston 5.
  • This diameter d Dw determines the hydrostatic force effect, which arises due to the pressure prevailing in the pressure compensator spring chamber 24 pressure due to the surface d Dw 2 ⁇ ⁇ / 4, because this area is the effective control pressure surface.
  • the inner diameter of the pressure compensator piston 5 is also shown and designated d I. To what extent this inner diameter d I is significant, will be explained.
  • a working position of the directional control valve piston 3 is shown.
  • the directional control valve piston 3 is displaced within the valve housing 1 to the left.
  • Hydraulic medium can now flow from the pump pressure ring channel P through the second valve piston radial opening 22 of the directional control valve piston 3 and through the radial opening 31 of the pressure balance piston 5 in the interior 7 of the pressure balance piston 5 and from there further into the axial bore 4 of the directional control valve piston 3 and further through the first valve piston radial opening 21 in the working port annular channel B.
  • the possible flow of the hydraulic medium is characterized by three dotted lines, from which it can be seen that the flow of hydraulic medium over the entire free Cross-section in the interior 7 of the pressure balance piston 5 and distributed in the axial bore 4 of the directional control valve piston 3.
  • the channels present in the valve housing 1 are always circumferential annular channels, the flow of the hydraulic medium is distributed over the entire annular surfaces.
  • the inner diameter D I of the pressure compensating piston 5 is relatively large, with the result that the flow velocity in the interior 7 of the pressure compensating piston 5 is relatively small.
  • This also applies to the flow in the axial bore 4 of the directional valve piston 3. Because of the low flow velocity, the hydrodynamic forces are small. This causes in accordance with the task, that the pressure compensator insensitive is against caused by different flow rates different flow forces.
  • the pressure balance piston 5 opens the connection between the valve piston radial opening 21 and the axial bore 4 of the directional control valve piston 3 via its control ribs 10 so that a certain outflow cross section results at the valve piston radial opening 21. If the pressure in the working port-ring channel B, according to the pressure at the corresponding load terminal of the consumer, is high and the resulting pressure force on the pressure balance piston 5, the sum of the pressure in the pressure compensator spring chamber 24 and the force of the pressure compensating spring 6 overcomes, then the pressure accumulates in the interior 7 of the pressure compensator piston 5 to the pressure in the working port-ring channel B and moves the pressure compensating piston 5 against the pressure compensating spring 6 as far to the right, as shown in FIG.
  • the pressure compensator spring chamber 24 is connected to the interior 7 of the pressure balance piston 5.
  • the pressure in the load-sensing annular channel LS follows this value because of the connection from the interior 7 of the pressure compensating piston 5 via the connecting bores 23 to the load-sensing annular channel LS.
  • the movement of the consumer is now carried out in a known manner by the action of a pump controller, not shown.
  • the pump governor raises the pump pressure just enough that the pressure drop across the set throttle cross-section of the second valve piston radial opening 22 of the directional control valve piston 3 is exactly the same as the difference "pump pressure minus control pressure" specified on the pump regulator.
  • a second step of the pressure compensator control takes place when the pressure in the working port annular channel B, corresponding to the pressure at the corresponding load port of the consumer, is less than the pump pressure.
  • the inner diameter d I of the pressure balance piston 5 is meaningful.
  • the maximum flow of the hydraulic medium through the pressure compensator is obtained when the largest effective opening cross section for the radial opening 22 is given by the relative position of the second valve piston radial opening 22 of the directional control valve piston 3 to the pump pressure annular channel. If the inner diameter d I of the pressure compensating piston 5 is large, a small axial flow velocity results in the interior 7 of the pressure compensating piston 5 with correspondingly low blasting forces. It has proven to be advantageous if the inner diameter d I is dimensioned so that the area d I 2 ⁇ ⁇ / 4 is about three to five times the area of the radial opening 22.
  • the pressure compensator spring chamber 24 is fundamentally and always in communication with the load-sensing annular channel LS.
  • the pressure in the interior 7 of the pressure balance piston 5 may be different depending on the working position of the directional control valve piston 3. In the neutral position shown in FIG. 1, it is indefinite. In order to achieve that even in this position the interior 7 of the pressure compensating piston 5 has a defined pressure, it is advantageous to provide a pressure relief bore 40 through which in the neutral position of the directional control valve piston 3, the axial bore 4 of the directional valve piston 3 and thus also the interior 7 of the Pressure compensating piston 5 is connected to the tank port ring channel T.
  • the interior 7 of the pressure compensator piston 5 is thus connected to the tank port ring channel T connectable, but only in the neutral position. Because the pressure in the tank connection ring channel T in the operation of the consumer is generally smaller than the pressure in the load-sensing ring channel LS, is thus achieved that pressure compensator piston 5 not only due to the action of the pressure compensating spring 6 assumes the desired unique position, but by the Pressure difference between load-sensing ring channel LS and tank connection ring channel T is still supported. Problems due to leakage pressure losses can not arise in this way.
  • a special shape of the end face 12 with the cross-sectional widening 13 of the axial bore 4 in the directional valve piston 3 is shown.
  • the central part of the end face 12 has the shape of a very flat cone 50 with a point angle of 150 to 170 degrees.
  • the conical part is adjoined by an annular surface 51 which is parallel to the axis of symmetry S s and then merges into an ellipsoid of revolution surface 52 which surrounds the cross-sectional widening 13.
  • This particular shape has beneficial influence on the flow in the axial bore 4 and provides means for deflecting the flow. As is known, an incoming or outgoing jet produces an undesirable resultant axial force component when the directions of entry and exit are different.
  • FIG. 5 shows a variant embodiment for that end of the pressure compensating piston 5 on which the control edge 30 is located.
  • FIGS. 6 a) to 6 c Alternative embodiments are shown in FIGS. 6 a) to 6 c).
  • Fig. 6 a) corresponds to the embodiment according to FIGS. 1 to 3
  • Fig. 6 b) and 6 c) show alternative embodiments.
  • Fig. 6 b) shows triangular spaces and the Fig. 6 c) circular segment-shaped spaces.
  • the embodiments according to FIGS. 5 and 6 a) to 6 c) thus show means on the control edge 30 of the pressure compensating piston 5 with which the dependence of the effective opening cross section during displacement of the pressure compensating piston 5 can be influenced in an advantageous manner. To achieve special opening characteristics, the different possibilities can also be combined.
  • FIGS. 1 and 3 only one half of the valve housing 1 and the directional control valve piston 3 is shown in each case. From the symmetry with respect to the vertical axis of symmetry S s it follows that even in the non-illustrated second half of the directional valve piston 3, a pressure compensating piston 5 of exactly the same design is included. It follows that in hydraulic consumers with two Ulau Bachn each of the working ports is assigned an individual pressure compensator.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Safety Valves (AREA)
  • Gas Exhaust Devices For Batteries (AREA)

Claims (8)

  1. Distributeur ou vanne à tiroir avec balance de pression ou manométrique située à l'intérieur, dont le corps de distributeur (1) présente un alésage longitudinal (2) dans lequel sont creusés des canaux annulaires (A, T, B, P, LS, E), dans lequel un piston de distributeur (3) est déplaçable axialement dans cet alésage longitudinal (2), lequel piston de distributeur (3) est constitué comme un tiroir creux équipé d'une première et d'une deuxième ouvertures radiales de piston de distributeur (21, 22) et présente un alésage axial (4) dans lequel un piston de balance de pression (5) équipé d'une arête de distribution (30) est déplaçable axialement contre un ressort de balance de pression (6), lequel piston de balance de pression (5) est constitué comme un tiroir creux avec un intérieur (7) présentant un diamètre DI et présente au moins une ouverture radiale (31) qui est disposée de manière à être en communication permanente avec la deuxième ouverture radiale de piston de distributeur (22), des moyens étant prévus en outre pour mettre une chambre de ressort de balance de pression (24) en communication permanente avec le canal annulaire Load Sensing (ou à détection de charge) (LS),
    caractérisé par le fait
    - que l'ouverture radiale (31) du piston de balance de pression (5) est disposée de manière à ce qu'une communication entre l'intérieur (7) et le canal annulaire de pression de pompe (P) puisse être ouverte à travers cette ouverture radiale (31) et la deuxième ouverture radiale de piston de distributeur (22),
    - que la deuxième ouverture radiale de piston de distributeur (22) constitue une arête de distribution par laquelle une communication entre l'intérieur (7) et le canal annulaire Load Sensing (LS) peut être ouverte, et
    - que la deuxième ouverture radiale de piston de distributeur (22) est immédiatement suivie d'une rainure annulaire (41) qui, dans la position neutre, établit une communication entre l'intérieur (7) et le canal annulaire Load Sensing (LS).
  2. Distributeur selon la revendication 1, caractérisé par le fait que la deuxième ouverture radiale de piston de distributeur (22) est disposée à l'extrémité du piston de balance de pression (5).
  3. Distributeur selon la revendication 1 ou 2, caractérisé par le fait que l'arête de distribution (30) du piston de balance de pression (5) est disposée à l'extrémité frontale du piston de balance de pression (5) qui est située à l'opposé de l'extrémité frontale du piston de balance de pression (5) qui est attaquée par le ressort de balance de pression (6) et où la pression agit dans la chambre de ressort de balance de pression (24).
  4. Distributeur selon l'une des revendications 1 à 3, caractérisé par le fait que le piston de distributeur (3) comporte un alésage de décharge de pression (40) à travers lequel l'alésage axial (4) du piston de distributeur (3) et par conséquent l'intérieur (7) du piston de balance de pression (5) peut être mis en communication avec le canal annulaire de réservoir (T), mais est seulement en communication dans la position neutre du distributeur.
  5. Distributeur selon l'une des revendications 3 à 4, caractérisé par le fait que des moyens (13, 50, 51, 52) pour dévier l'écoulement sont disposés au niveau de la surface frontale (12) de l'alésage axial (4) du piston de distributeur (3).
  6. Distributeur selon la revendication 5, caractérisé par le fait que les moyens (13, 50, 51, 52) pour dévier l'écoulement sont constitués par un cône très plat (50) qui forme la partie centrale de la surface frontale (12), auquel fait suite une surface annulaire (51) qui se situe parallèlement à un axe de symétrie Ss et passe à une surface ellipsoïdale de révolution (52) qui entoure un élargissement de section (13).
  7. Distributeur selon l'une des revendications 3 à 6, caractérisé par le fait que le diamètre intérieur DI du piston de balance de pression (5) est dimensionné de manière à ce que la surface dI 2 · π/4 soit à peu près comprise entre le triple et le cinquième de la surface de l'ouverture radiale 22.
  8. Distributeur selon l'une des revendications 3 à 6, caractérisé par le fait que l'arête de distribution (30) du piston de balance de pression (5) est formée par des moyens particuliers de manière à ce que la dépendance de la section d'ouverture efficace soit influençable lors du déplacement du piston de balance de pression (5).
EP02727817A 2001-04-17 2002-03-13 Tiroir a balance manometrique situee a l'interieur Expired - Lifetime EP1381779B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH6992001 2001-04-17
CH6992001 2001-04-17
PCT/IB2002/000759 WO2002088550A1 (fr) 2001-04-17 2002-03-13 Tiroir a balance manometrique situee a l'interieur

Publications (2)

Publication Number Publication Date
EP1381779A1 EP1381779A1 (fr) 2004-01-21
EP1381779B1 true EP1381779B1 (fr) 2006-05-17

Family

ID=4529886

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02727817A Expired - Lifetime EP1381779B1 (fr) 2001-04-17 2002-03-13 Tiroir a balance manometrique situee a l'interieur

Country Status (5)

Country Link
US (1) US6860291B2 (fr)
EP (1) EP1381779B1 (fr)
AT (1) ATE326636T1 (fr)
DE (1) DE50206817D1 (fr)
WO (1) WO2002088550A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007026421A1 (de) * 2007-06-06 2008-12-11 Zf Friedrichshafen Ag Servounterstützungseinrichtung
US8578809B2 (en) 2007-06-06 2013-11-12 Zf Friedrichshafen Ag Shifting device for a variable speed motor vehicle transmission

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009010331A1 (fr) * 2007-07-18 2009-01-22 Schaeffler Kg Élément d'une soupape de commande pour la commande de flux de fluide sous pression
DE102007054134A1 (de) 2007-11-14 2009-05-20 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
US20140165767A1 (en) * 2012-12-19 2014-06-19 Deere And Company Manual synchronized gear shift assist
DE102018001303A1 (de) * 2018-02-20 2019-08-22 Hydac Fluidtechnik Gmbh Ventilvorrichtung
DE102019214685A1 (de) * 2019-09-25 2021-03-25 Zf Friedrichshafen Ag Gehäuse für ein Ventil

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4719753A (en) * 1985-02-22 1988-01-19 Linde Aktiengesellschaft Slide valve for load sensing control in a hydraulic system
EP0593782B1 (fr) * 1992-04-20 1998-07-01 Hitachi Construction Machinery Co., Ltd. Dispositif a circuit hydraulique destine aux machines de chantier
DE19836564B4 (de) 1998-08-12 2005-12-29 Bosch Rexroth Aktiengesellschaft Ventilanordnung
DE19855187A1 (de) 1998-11-30 2000-05-31 Mannesmann Rexroth Ag Verfahren und Steueranordnung zur Ansteuerung eines hydraulischen Verbrauchers

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007026421A1 (de) * 2007-06-06 2008-12-11 Zf Friedrichshafen Ag Servounterstützungseinrichtung
US8578809B2 (en) 2007-06-06 2013-11-12 Zf Friedrichshafen Ag Shifting device for a variable speed motor vehicle transmission

Also Published As

Publication number Publication date
EP1381779A1 (fr) 2004-01-21
DE50206817D1 (de) 2006-06-22
ATE326636T1 (de) 2006-06-15
US20040094210A1 (en) 2004-05-20
US6860291B2 (en) 2005-03-01
WO2002088550A1 (fr) 2002-11-07

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