EP2220378B1 - Vanne hydraulique - Google Patents

Vanne hydraulique Download PDF

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Publication number
EP2220378B1
EP2220378B1 EP20080802277 EP08802277A EP2220378B1 EP 2220378 B1 EP2220378 B1 EP 2220378B1 EP 20080802277 EP20080802277 EP 20080802277 EP 08802277 A EP08802277 A EP 08802277A EP 2220378 B1 EP2220378 B1 EP 2220378B1
Authority
EP
European Patent Office
Prior art keywords
valve
pocket
channels
pressure line
connection
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.)
Not-in-force
Application number
EP20080802277
Other languages
German (de)
English (en)
Other versions
EP2220378A1 (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.)
Hydac Filtertechnik GmbH
Original Assignee
Hydac Filtertechnik 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 Hydac Filtertechnik GmbH filed Critical Hydac Filtertechnik GmbH
Publication of EP2220378A1 publication Critical patent/EP2220378A1/fr
Application granted granted Critical
Publication of EP2220378B1 publication Critical patent/EP2220378B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—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
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86622—Motor-operated
    • Y10T137/8663—Fluid motor
    • 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
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86879—Reciprocating valve unit

Definitions

  • the invention relates to a hydraulic valve device, in particular in the manner of at least one LS-way valve according to the feature configuration of the preamble of claim 1.
  • WO 2006/105765 A1 is a LS-way valve with two guided in a valve bore coaxially arranged valve spools, which are stretched towards each other in a basic position via a Zentrierfederan eleven, and for setting a certain slide position from the basic position in the two adjacent faces of the valve spool without interposition of elastic support elements abut each other or adjacent to each other, are movable apart, which are displaceable together for setting further working positions, wherein the end faces for moving in the slide position can be acted upon by a common control pressure, which is also on remote from the end faces, with lower effective area running rear control surfaces the valve spool acts.
  • a generic hydraulic valve device is known, in particular in the manner of at least one LS-way valve, with a valve housing and a longitudinally movable arranged control slide for driving a fluid connection arrangement consisting of at least one inlet connection, a return connection, a load-sensing connection, a working connection and at least a control pressure line and at least one supply pressure line, wherein at least for a load-sensing connection, for a control pressure line and a supply pressure line a pocket-like channel between the valve housing and spool is arranged.
  • the known solution has the goal to provide a valve spool device which is particularly short and narrow and can be designed simply and yet achieves a fully satisfactory functioning, the known solution leaves just in reaching the pending goals still wishes.
  • the present invention seeks to provide a structurally simple valve device, which is considered small in particular in the direction of the spool axis constructive and manages with little usable components and in this respect proves to be particularly reliable.
  • This object is achieved by a valve device with the features of claim 1 in its entirety.
  • the pocket-like channels are seen in a cross section through valve housing and spool at uniform radial intervals around the spool around, results in a smaller number of functional components, so that the inventive solution also less disturbing and is susceptible to wear, and as far as a reliable and long-lasting operation is guaranteed. Since, due to the solution according to the invention, the structural components to be used within the valve device are reduced, space can be saved.
  • said annular channel in the housing is divided into three independent pairs of pockets, which are distributed symmetrically on the circumference relative to the longitudinal axis of the spool.
  • the first pocket pair assumes the function of forwarding the LS pressure from the spool valve to the LS signaling chain in the valve housing.
  • the second pair of pockets is permanently connected to the control pressure line P ST and the third pair of pockets, which is connected to a supply pressure line Y, can be connected via the possible spool stroke with the second pair of pockets and the pertinent space-saving arrangement allows a variety of hydraulic functions to be performed.
  • the hydraulic valve device according to the invention is in its basic structure in the forth Fig.1 shown. However, that is Fig.1 in so far as a simplified representation, as it does not specify the other valve components, as they usually belong to such hydraulic valve devices and as exemplified in the DE 199 19 014 A1 as well as the WO 2006/105765 A1 are shown.
  • the valve device is in particular in the form of a so-called.
  • LS directional control valve formed with a valve housing 10 and a longitudinally movable arranged spool 12 for driving a designated as a whole 14 Fluidanschlußan extracting of at least one inlet port P, a submittaufanschlapt R, a load-sensing connection LS, a working port A, B and a control pressure line P ST and a supply pressure line Y.
  • the inlet connection P occurs twice and forms the usual pressure supply connection, ie by means of a hydraulic pump, not shown, the valve device can be supplied with pressurized fluid of predeterminable amount.
  • two working ports A, B are provided, for example, with a not closer shown working device of a hydraulic device, for example in the form of a hydraulic steering or working cylinder, are in fluid-carrying operative connection to leave the pertinent hydraulic cylinder for a working activity and retract.
  • the left half of the picture in viewing direction on the Fig.1 shows, for the load-sensing connection LS and the control pressure line P ST and the supply pressure line Y at least one pocket-like channel 18 between the valve housing 10 and spool 12 is arranged.
  • the aforementioned pocket-like channels 18 are thus arranged in the mentioned cross-section at uniform radial intervals around the spool 12 around.
  • the pocket-like channels are divided into three independent pairs of pockets, wherein the first pair of pockets assumes the function of forwarding the LS pressure from the spool 12 in the LS message chain 20 in the housing.
  • the second pair of pockets is permanently connected to the control pressure line P ST (control oil circuit).
  • the third pair of pockets which forwards the Y-fluid pressure via the supply line Y, can be connected via the spool stroke to the second pair of pockets.
  • each pair partner is diametrically opposed to the other partner, in relation to the longitudinal axis of the control slide 12, in the adjacent valve housing 10. Furthermore, it is true that always only one pocket has a forwarding connection in the housing 10. For a symmetrical pressure load of the spool 12 has this pressure equalization connections from the connected housing pocket of a pair to the opposite housing pocket, which forms only a sealed pressure chamber, which will be explained in more detail in detail.
  • the pressure equalization connections therefore always connect only one pair of pockets each without crossing.
  • the orientation of the pressure equalization connections in the control slide 12 to the said pairs of housing pockets in the form of the longitudinal channels 18 is maintained by a non-illustrated mechanical anti-rotation of the slider 12 to the housing 10.
  • the shows Fig.1 in that the pocket-like channels 18 are arranged parallel to the displacement axis of the control slide 12 and are guided as longitudinal channels in the valve housing 10, spatially between the direction of view of the latter Fig.1 Left inlet port P and the left chamber 22 for the control pressure of the spool valve to bring it into a right position.
  • the control chamber is designed pressure-tight by a drive head, not shown. In the floating position of the spool shown here, the left control chamber is depressurized and the right is acted upon by control pressure.
  • the pockets shown for the pressures LS, P ST and Y are introduced into the bore wall of the spool bore.
  • each pocket-like longitudinal channel 18 is assigned a compensation channel 24 which are fluid-tightly separated from each other and make the pressure equalization for each assignable pocket pair, wherein at least part of the compensation channels 24, this from their fluid receiving volume ago, for example due to the length the channel guide, different from each other.
  • the said holes may but do not intersect fluidly, otherwise no separate pressure levels in the individual pocket-like channels 18 can be sealed.
  • the interior of the spool 12 is therefore according to the illustration of the Figure 4 introduced a kind of labyrinth pin 26 whose lateral surface the compensation channels 24 (see. Figure 6 ) in order to enable these intersection-free connections at all.
  • the radial pressure equalization holes in the spool 12 each end on the outer surface of the labyrinth pin 26 except the load sensing holes LS A ; These go through a vertical labyrinthine guide in the labyrinth pin 26 from one side directly to the diametrically opposite opposite side relative to the longitudinal axis of the bolt 26.
  • the holes of the load sensing line LS B in turn end on an annular groove, which pass over two longitudinal grooves between the through holes.
  • the otherwise cylindrical labyrinth pin 26 is guided in a cylindrical inner recess of the spool 12, which is provided to the outside with load sensing and load-sensing terminals 27 for the Nutzan say A, B.
  • the in the Figure 3 shown sectional or cross-sectional view is placed from its axial position forth at the height of the pockets P ST , LS and Y.
  • the aforementioned pockets in the form of the longitudinal channels 18 can be produced by a cutting tool which cuts in radially via a radially dipping cutter.
  • two opposite pockets each have the same pressure level as a pocket pair.
  • each one of the pockets in the form of a longitudinal channel 18 of a pair has a line connection in the housing 10.
  • the control oil P ST top the Y port at 10 o'clock and the LS port at 8 o'clock, if one Clock dial in the figurative sense on the representation after the Figure 3 would apply.
  • a seat-tight check valve 28 is arranged. It is held by a compression spring 30 in the closed position as shown in the Fig.1 , wherein two control units 32 in the form of pressure-shaped actuators can cause the switching operation for the check valve 28. Furthermore, the so-called. Spring side of the check valve 28 via a throttle 34 is constantly connected to the load pressure of the working port A.
  • a pilot valve 26 is used, which can be controlled via a Y-switching pressure in the pertinent supply pressure line Y. If the said Y pressure is switched through the spool 12, then the Y pressure acts on a large control surface against the load pressure on a small control surface, the design force Y and the control surface exceeding the maximum closing force. With open pilot valve 36 then flows a continuous control oil flow from the load of the hydraulic load at the Nutzanschluß A via the throttle 34 and via the pilot valve 36 into a tank port T from. At the throttle 34 then drops such a high pressure that the spring side of the seat-tight check valve 28 falls to a pressure level near the tank pressure. Now, the load pressure on the opposite side of the spring can overcome the resultant force-out and low compression force and lift the seat piston (not shown) as part of the hydraulic load.
  • the spool 12 is in the Fig.1 shown in the so-called. Floating position, in which the inlet port P is locked and the working ports A and B are connected to the return R.
  • the control pressure Y derived from the control pressure P ST is switched through in this position to the pilot valve 36 and unlocks said pilot valve 36.
  • the pilot valve 36 and the check valve 28 are shown in the closed position.
  • the pilot pressure Y can be selectively generated for a pilot operated check valve at port A or B or both. It is also possible to save space to save at least the pilot-operated check valve 28 in the slide axis.
  • the spool 12 could have integrated switching or proportional valves that are pilot operated with pressures generated outside the control axis, or vice versa, it would be possible for valves integrated in the spool to direct a control pressure into the housing 10 without causing it to elongate in the cases described herein the valve axis and thus the length of the valve device would come.
  • FIG. 7 shows Figure 7 the cross-sectional arrangement of two-way valves as shown in the Figure 3 in section construction for the realization of a kind of safety circuit by the mutual release of the control oil supply for the left neighbor valve 38 and the right neighbor valve 40, which are both bordered by standard valve components 42.
  • the control oil pressure P ST is switched through to the supply line VL of the right neighbor valve 40.
  • this connection is interrupted by the spool stroke of the left neighbor valve 38 and the electro-hydraulic pilot valves of the right neighbor valve 40 can not build a driving pressure.

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

Claims (7)

  1. Dispositif de vanne hydraulique, notamment à la manière d'au moins un distributeur LS, comprenant un corps (10) de vanne et un tiroir (12) de commande qui y est monté mobile longitudinalement pour commander un dispositif (14) de raccord de fluide constitué d'au moins,
    - un raccord (P) d'afflux,
    - un raccord ( R ) de reflux,
    - un raccord load-sensing (LS),
    - un raccord (A, B) de travail ainsi que
    ayant au moins un conduit (PST) de pression de commande et au moins un conduit (Y) de pression d'alimentation, dans lequel au moins pour un raccord load-sensing (LS), pour un conduit (PST) de pression de commande et pour un conduit (Y) de pression d'alimentation un canal (18) de type à poche est monté entre le corps (10) de vanne et le tiroir (12) de commande, caractérisé en ce que les canaux (18) de type à poche sont disposés, considéré dans une section transversale du corps (10) de vanne et du tiroir (12) de commande, à des intervalles radiaux uniformes autour du tiroir (12) de commande.
  2. Dispositif de vanne suivant la revendication 1, caractérisé en ce que les canaux (18) de type à poche, en étant disposés parallèlement à l'axe de déplacement du tiroir (12) de commande sous la forme de canaux longitudinaux, sont guidés dans le corps (10) de vanne et, considéré dans l'espace, entre un raccord (P) d'afflux et une chambre de pression pour la pression de commande du tiroir (12) de commande.
  3. Dispositif de vanne suivant la revendication 1 ou 2, caractérisé en ce qu'au raccord load-sensing (LS), au conduit (PST) de pression de commande et au conduit (Y) de pression d'alimentation sont associés respectivement par paire des canaux (18) de type à poche, qui sont opposés diamétralement par rapport à l'axe longitudinal du corps (10) de la vanne.
  4. Dispositif de vanne suivant la revendication 2 ou 3, caractérisé en ce que dans le tiroir (12) de commande il y a, associé à chaque canal (18) longitudinal de type à poche, un canal (24) de compensation, lesquels sont séparés d'une manière étanche au fluide les uns des autres et effectuent une compensation de pression pour une paire de poches et en ce qu'au moins une partie des canaux (24) de compensation se distinguent les uns des autres par leur volume de réception de fluide.
  5. Dispositif de vanne suivant l'une des revendications 2 à 4, caractérisé en ce que, pour obtenir une orientation constante de liaisons de compensation de pression entre elles, formées des canaux (18) longitudinaux et des canaux (24) de compensation associés, il est prévu un dispositif mécanique de sécurité à la torsion entre le tiroir (12) de commande et le corps (10) de la vanne.
  6. Dispositif de vanne suivant l'une des revendications 1 à 5, caractérisé en ce qu'entre un consommateur hydraulique et un raccord (A, B) utile pouvant lui être associé est monté un clapet anti-retour (28) qui peut être commandé par une vanne (36) pilote, laquelle est raccordée pour sa commande au conduit (Y) de pression d'alimentation.
  7. Dispositif de vanne suivant l'une des revendications 1 à 6, caractérisé en ce que, pour la réalisation d'un circuit de sécurité, au moins deux distributeurs sont reliés entre eux en assemblage de bloc de manière à ce que, dans tous les cas, le conduit (Y) de pression d'alimentation respectif de l'un des distributeurs puisse être relié à des conduits (VL) d'alimentation d'au moins une vanne (36) pilote électrohydraulique.
EP20080802277 2007-11-14 2008-09-17 Vanne hydraulique Not-in-force EP2220378B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710054138 DE102007054138A1 (de) 2007-11-14 2007-11-14 Hydraulische Ventilvorrichtung
PCT/EP2008/007749 WO2009062563A1 (fr) 2007-11-14 2008-09-17 Vanne hydraulique

Publications (2)

Publication Number Publication Date
EP2220378A1 EP2220378A1 (fr) 2010-08-25
EP2220378B1 true EP2220378B1 (fr) 2012-09-12

Family

ID=40210560

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20080802277 Not-in-force EP2220378B1 (fr) 2007-11-14 2008-09-17 Vanne hydraulique

Country Status (5)

Country Link
US (1) US8453679B2 (fr)
EP (1) EP2220378B1 (fr)
JP (1) JP2011503478A (fr)
DE (1) DE102007054138A1 (fr)
WO (1) WO2009062563A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009021103A1 (de) * 2009-05-13 2010-11-18 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
DE102013014671A1 (de) 2013-09-03 2015-03-05 Hydac Technology Gmbh Ventilbaukomponenten
EP3431843B1 (fr) * 2017-07-18 2020-05-06 Hamilton Sundstrand Corporation Tiroir de valve
US11680649B2 (en) * 2020-11-16 2023-06-20 Parker-Hannifin Corporstion Proportional valve spool with linear flow gain

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2939429A (en) * 1957-10-21 1960-06-07 Germane Corp Rotary valve for power steering mechanism
US3177897A (en) * 1961-09-18 1965-04-13 New York Air Brake Co Pressure reducing and distributing valve
DE1648012B1 (de) 1967-04-27 1972-05-31 Heilmeier & Weinlein Mengengeregelte Steuerschiebervorrichtung
DE19919014C2 (de) 1999-04-27 2001-03-01 Danfoss Fluid Power As Nordbor Hydraulikventil mit einer Verriegelungs- und einer Schwimmfunktion
DE102005005927A1 (de) * 2005-02-09 2006-08-17 Bosch Rexroth Aktiengesellschaft Hydraulische Steueranordnung
DE102005029821A1 (de) 2005-04-04 2006-10-05 Bosch Rexroth Ag Wegeventil und damit ausgeführte LS-Steueranordnung
DE102005050169A1 (de) * 2005-06-21 2006-12-28 Bosch Rexroth Ag LS-Steueranordnung und LS-Wegeventil

Also Published As

Publication number Publication date
EP2220378A1 (fr) 2010-08-25
DE102007054138A1 (de) 2009-05-28
US20100206413A1 (en) 2010-08-19
JP2011503478A (ja) 2011-01-27
WO2009062563A1 (fr) 2009-05-22
US8453679B2 (en) 2013-06-04

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