EP0618372A2 - Dispositif hydraulique de commande avec au moins un clapet anti-retour piloté - Google Patents

Dispositif hydraulique de commande avec au moins un clapet anti-retour piloté Download PDF

Info

Publication number
EP0618372A2
EP0618372A2 EP94102873A EP94102873A EP0618372A2 EP 0618372 A2 EP0618372 A2 EP 0618372A2 EP 94102873 A EP94102873 A EP 94102873A EP 94102873 A EP94102873 A EP 94102873A EP 0618372 A2 EP0618372 A2 EP 0618372A2
Authority
EP
European Patent Office
Prior art keywords
piston
valve
control device
unlocking piston
unlocking
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
EP94102873A
Other languages
German (de)
English (en)
Other versions
EP0618372B1 (fr
EP0618372A3 (fr
Inventor
Michel Duby
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0618372A2 publication Critical patent/EP0618372A2/fr
Publication of EP0618372A3 publication Critical patent/EP0618372A3/fr
Application granted granted Critical
Publication of EP0618372B1 publication Critical patent/EP0618372B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F15B13/015—Locking-valves or other detent i.e. load-holding devices using an enclosed pilot flow valve

Definitions

  • the invention relates to a hydraulic control device with at least one hydraulically unlockable check valve according to the preamble of the main claim.
  • Control devices of this type which are also referred to as a hydraulic blocking block or an unlockable twin check valve, are generally connected between a double-acting hydraulic consumer and a 4/3-way valve in order to provide a hydraulically safe shut-off of the loaded consumer by a directional valve with leakage losses to achieve check valves designed as seat valves.
  • the two pilot-operated check valves and the free-floating unlocking piston assigned to them are located coaxially to one another in a continuous longitudinal bore in the housing, the unlocking piston with a central piston section in the longitudinal bore is tight and slidable and hydraulically separates the two hydraulic connections via the check valves.
  • the distance between these two pressure medium connections is limited, which results in a mostly short axial construction of the central piston section, the guide length of which is usually only slightly larger than its diameter.
  • Relatively long, bolt-shaped lugs protrude from the piston section to the two check valves in order to enable mechanical unlocking.
  • a disadvantage of this type of control devices is that the guide length of the unlocking piston in the longitudinal bore is relatively short due to connection standards or other structural conditions.
  • the hydraulic control device according to the invention with at least one hydraulically unlockable check valve and with the characterizing features of the main claim has the advantage that it is less susceptible to wear, especially under heavy loads, and thereby achieves a longer service life.
  • the control device builds with relatively little effort, simple and compact.
  • the additional guide point of the unlocking piston in the immediate vicinity of the check valve allows the The forces acting on the locking piston are transferred to the housing much better.
  • the flow resistance in the two pressure medium connections is only slightly increased by the guide webs on the unlocking piston, so that the function of the locking block is not adversely affected.
  • the guide length of the unlocking piston can now correspond to almost its entire length. Leakage problems on the unlocking piston caused by wear and the associated failure of the control device are avoided.
  • FIG. 1 shows a longitudinal section through a first hydraulic control device in a simplified representation
  • FIG. 2 shows a front view of the unlocking piston according to FIG. 1
  • FIG. 3 shows a side view of the unlocking piston according to FIG. 2
  • FIG. 4 shows a second embodiment of the unlocking piston for the control device according to FIG. 1.
  • FIG. 1 shows a simplified representation of a longitudinal section through a control device 10, which essentially consists of two hydraulically unlockable check valves 11 and 12 and an associated hydraulically actuated unlocking piston 13.
  • the control device 10 has a continuous longitudinal bore 15 in a block-shaped housing 14, in which two internal valve chambers 16, 17 and two motor chambers 18, 19 adjoining it on the outside are formed symmetrically to one another by annular extensions.
  • a valve seat 21 or 22 which is fixed to the housing is formed and which is assigned to the respective outer seat valve bodies 23 or 24 of the first or second check valve 11, 12.
  • the two motor chambers 18, 19 are connected via inclined channels in the housing 14 to motor connections 25 and 26, to which a double-acting hydraulic motor 27 is connected.
  • the two internal valve chambers 16, 17 are connected to valve connections 28 and 29, to which a conventional 4/3-way valve 31 is connected.
  • the longitudinal bore 15 in the housing 14 is formed in the area between the two valve seats 21, 22 with the same diameter and has a central, cylindrical section 32 delimited by the two valve chambers 16, 17, in which the unlocking piston 13 is sealed with a cylindrical piston section 33 is slidably guided.
  • the piston section 33 thus hydraulically separates the two pressure medium connections from the directional control valve 31 to the motor 27.
  • the longitudinal bore 15 has cylindrical bore sections 34 and 35, respectively, in the area between the engine chamber 18 and 19 and the valve chamber 16 and 17, respectively, against which the valve seats 21 and 22 abut.
  • the unlocking piston 13 is now additionally guided in the immediate vicinity of the first check valve 11, in that guide webs 36 are formed at its end remote from the piston section 33.
  • FIG. 1 in conjunction with FIGS. 2 and 3 three such guide webs 36 are arranged in a star shape on the unlocking piston 13 and are therefore evenly distributed along the circumference.
  • the guide webs 36 have a cylindrical outer surface 37 with which they are guided in the bore section 37 and can be supported there.
  • a relatively deep annular groove 38 is machined into the guide webs 36, the inner diameter of which is approximately the same as the core diameter of the unlocking piston 13 and the axial width of which is approximately one third of the axial length of the guide webs 36.
  • the unlocking piston 13 then has a bolt-shaped end 41 on the guide webs 36, which has a relatively short construction and is used to mechanically unlock the pilot-operated check valve 11.
  • the guide webs 36 are thus in the immediate vicinity of the check valve 11 and form an additional guide for the end of the unlocking piston 13 within the bore section 34.
  • the axial length of the guide webs 36 is greater than the axial width of the first valve chamber 16, so that in each Position of the unlocking piston 16 permanent guidance is maintained.
  • the unlocking piston 13 of the control device 10 is formed in one piece and constructed symmetrically with respect to its central piston section 33, so that corresponding guide webs 42, which are guided in the second bore section 35, are arranged corresponding to the first guide webs 36 at one end of the unlocking piston 13 at its opposite end are.
  • the unlocking piston 13 is thus mounted three times in the longitudinal bore 15.
  • control device 10 The mode of operation of the control device 10 is explained as follows, the basic function of such a blocking block being assumed to be known per se.
  • the free-floating unlocking piston 13 When the directional control valve 31 is not actuated, the free-floating unlocking piston 13 is held in its central position by the closed check valves 11 and 12 and the motor 27 is shut off hydraulically by the check valves 11, 12 designed as seat valves. If pressure medium is actuated via the second valve connection 29 and the hydraulically opened second check valve 12 to the motor 27 when the directional valve 31 is actuated, the pressure building up in the second valve chamber 17 acts on the unlocking piston 13 and pushes it to the left, based on FIG During this left movement of the unlocking piston 13, the pilot-operated first check valve 11 is mechanically unlocked so that pressure medium can flow out from the other side of the motor 27 via the first motor connection 25, the check valve 11 and the first valve connection 28 to the directional control valve 31 and further to the tank.
  • the recesses 39 remaining between the star-shaped guide webs 36, 42 ensure that a relatively large flow cross-section is available for both the inflowing and the outflowing pressure medium flow in the region of the bore sections 35 and 34, so that no disturbing throttling is available occurs.
  • the relatively large ring grooves 38 additionally promote the inflow and outflow of the pressure medium.
  • the cylindrical lateral surfaces 37 of the guide webs 36 and 42 ensure that any radial forces can be transmitted from the unlocking piston 13 to the housing 14 during operation, so that no recognizable signs of wear occur even when the control device 10 is subjected to high loads.
  • the piston section 33 can take over a perfect seal, so that no disturbing leakage oil flows can build up between the two pressure medium connections. Even when the check valves 11 and 12 open on the unlocking piston 13, radial forces cannot adversely affect the operation of the control device 10.
  • the control device 10 therefore shows significantly fewer signs of wear, particularly under heavy loads, which considerably increases its service life.
  • FIG. 4 shows a front view of an unlocking piston 50 as a second embodiment, as can be used in the control device 10 instead of the one-piece unlocking piston 13 according to FIG.
  • the guide webs 36 are formed in the same way, while it has a narrower piston section 51.
  • the unlocking piston 50 thus represents one half of the one-piece locking piston 13 according to FIG. 2.
  • Two unlocking pistons 50 of this type can be installed with adjacent piston sections 51 in the housing 11 of the control device 10, so that the latter is functional in the same way.
  • the two-part design of the unlocking piston 50 according to FIG. 4 has the advantage that it is much easier to manufacture and that this unlocking piston 50 can also be used with single-acting locking blocks that only work with a single check valve.
  • control device is shown in connection with a double-acting locking block, it can also be used with a single-acting locking block.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Check Valves (AREA)
  • Valve Device For Special Equipments (AREA)
EP94102873A 1993-03-18 1994-02-25 Dispositif hydraulique de commande avec au moins un clapet anti-retour piloté Expired - Lifetime EP0618372B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9303988U DE9303988U1 (de) 1993-03-18 1993-03-18 Hydraulische Steuereinrichtung mit mindestens einem hydraulisch entsperrbaren Rückschlagventil
DE9303988U 1993-03-18

Publications (3)

Publication Number Publication Date
EP0618372A2 true EP0618372A2 (fr) 1994-10-05
EP0618372A3 EP0618372A3 (fr) 1995-03-01
EP0618372B1 EP0618372B1 (fr) 1998-10-07

Family

ID=6890805

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94102873A Expired - Lifetime EP0618372B1 (fr) 1993-03-18 1994-02-25 Dispositif hydraulique de commande avec au moins un clapet anti-retour piloté

Country Status (2)

Country Link
EP (1) EP0618372B1 (fr)
DE (2) DE9303988U1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19646428A1 (de) * 1996-11-11 1998-05-14 Rexroth Mannesmann Gmbh Ventilanordnung
EP1500825A3 (fr) * 2003-07-25 2005-05-11 Bosch Rexroth AG Distributeur à voies multiples
CN104533873A (zh) * 2015-01-05 2015-04-22 江苏真绩机械制造有限公司 双向自锁液压缸

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4461314A (en) * 1982-09-13 1984-07-24 Deere & Company Electrohydraulic valve

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19646428A1 (de) * 1996-11-11 1998-05-14 Rexroth Mannesmann Gmbh Ventilanordnung
DE19646428B4 (de) * 1996-11-11 2007-04-19 Bosch Rexroth Aktiengesellschaft Ventilanordnung
EP1500825A3 (fr) * 2003-07-25 2005-05-11 Bosch Rexroth AG Distributeur à voies multiples
CN104533873A (zh) * 2015-01-05 2015-04-22 江苏真绩机械制造有限公司 双向自锁液压缸

Also Published As

Publication number Publication date
DE9303988U1 (de) 1994-07-21
EP0618372B1 (fr) 1998-10-07
DE59407027D1 (de) 1998-11-12
EP0618372A3 (fr) 1995-03-01

Similar Documents

Publication Publication Date Title
DE3913460C2 (de) Hydraulisches Umsteuerventil
DE1601729B2 (de) Mit Vorsteuerung arbeitende hydraulische SteuerventUeinrichtung
DE2232864C3 (de) Steuerventil
WO1985003992A1 (fr) Distributeur
DE3104957C2 (de) Hydraulisch betätigbares Pressensicherheitsventil
DE2945911C2 (fr)
DE19514244A1 (de) Hydraulische Zahnstangenlenkung
DE2435685A1 (de) Zylinder-kolben-steuerventil
DE69524582T2 (de) Richtungssteuerventil
DE69601157T2 (de) Druckreduzierventil
DE3315056C2 (de) Elektrohydraulisches Mehrwege-Regelventil
EP0618372B1 (fr) Dispositif hydraulique de commande avec au moins un clapet anti-retour piloté
EP0342409A2 (fr) Soupape de sûreté
DE3817122A1 (de) Sicherheitsventil
DE68905659T2 (de) Hydraulischer radialkolbenmotor mit veraenderbarem hubvolumen.
DE4413216C2 (de) Hydraulisches Wegeventil
EP0943057A1 (fr) Distributeur pour la commande, independante de la charge, d'un consommateur hydraulique au niveau du sens et de la vitesse
EP0935716A1 (fr) Systeme de valve anti-retour
DE2807542C2 (de) Stromregelventil
DE19646428B4 (de) Ventilanordnung
DE4418514B4 (de) Elektrohydraulisches Wegeventil
DE2716694A1 (de) Steuereinrichtung fuer einen hydraulischen arbeitszylinder
DE29613700U1 (de) Druckverhältnisventil
DE3106532C2 (fr)
DE68916946T2 (de) Steuerungsventil.

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE FR IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE FR IT

17P Request for examination filed

Effective date: 19950901

17Q First examination report despatched

Effective date: 19970703

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR IT

REF Corresponds to:

Ref document number: 59407027

Country of ref document: DE

Date of ref document: 19981112

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20030221

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20030325

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040901

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20041029

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050225