WO1998005870A1 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique Download PDF

Info

Publication number
WO1998005870A1
WO1998005870A1 PCT/EP1997/003031 EP9703031W WO9805870A1 WO 1998005870 A1 WO1998005870 A1 WO 1998005870A1 EP 9703031 W EP9703031 W EP 9703031W WO 9805870 A1 WO9805870 A1 WO 9805870A1
Authority
WO
WIPO (PCT)
Prior art keywords
control
piston
pressure
control piston
consumer
Prior art date
Application number
PCT/EP1997/003031
Other languages
German (de)
English (en)
Inventor
Armin Stellwagen
Original Assignee
Mannesmann Rexroth Ag
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 Mannesmann Rexroth Ag filed Critical Mannesmann Rexroth Ag
Publication of WO1998005870A1 publication Critical patent/WO1998005870A1/fr

Links

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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F15B13/0403—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves a secondary valve member sliding within the main spool, e.g. for regeneration flow
    • 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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
    • 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
    • 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

Definitions

  • the invention relates to a hydraulic control device according to the preamble of claim 1.
  • control piston has sleeve-shaped extensions at its ends, which protrude into the control spaces for the control liquid and each have an axial and radial bore in the control piston with the closest one connected to the consumer connection
  • Volumetric pistons are guided in the sleeve-shaped extensions, which are supported on fixed housing stops when acted upon by the load pressure occurring in the controlled consumer.
  • the force resulting from this pressurization counteracts the force acting on the control piston from the control pressure for displacing the control piston into an opening position which determines the amount of working fluid from the pressure medium source to the consumer.
  • the cross-sectional area of the measuring piston acted upon by the load pressure must be of such a size that the resulting pressure force, in addition to the spring force of the springs returning the control piston to its initial position, is not greater than the maximum adjusting force by the control pressure of the control piston.
  • the load pressure is passed on to the control chamber of a pressure compensator assigned to the control piston or to the outside for connection to the adjusting device of a variable displacement pump via housing channels which branch off from the consumer connections.
  • the object of the invention is to simplify the housing of the control device by largely dispensing with the housing channels carrying the load pressure and, when using control pistons with two measuring pistons, two measuring pistons a common space loaded by the load pressure can be assigned.
  • 1 denotes the housing of a hydraulic control device.
  • a control piston 3 In a through bore 2, a control piston 3 is arranged, which consists of five sections 4, 5, 6, 7 and 8, which are interconnected by four webs 9, 10, 11 and 12.
  • the webs form control spaces 13, 14, 15 and 16 together with circumferential housing recesses.
  • the control space 15 is connected via a channel 17 and a pressure compensator 18 to the connection channel 19 for a variable displacement pump P and the control spaces 14 and 16 with connection channels (not shown) for the
  • a circumferential housing recess 20 is provided between the control rooms 14 and 15 and a circumferential housing recess 21 is provided between the control rooms 15 and 16.
  • the housing recess 20 is connected via a channel 22 to the working line connection A and the housing recess 21 via a channel 23 to the working line connection B, which in turn are connected via working lines AI, Bl to the working spaces ZI, Z2 of a consumer V designed as a differential cylinder .
  • the housing recesses 20, 21 are from control edges 24, 25, 26 and 27 limited, which cooperate with a corresponding axial displacement of the control piston with its fine control grooves 28, 29, 30, 31 and its circumferential control edges 32, 33, 34, 35.
  • the control piston 3 is traversed with an axial bore 36 which at its ends for receiving guide inserts 37, 38 for
  • volumetric flasks 39, 40 are expanded and provided with thread 41.
  • the control piston also has radial bores 42, 43 in the area of the fine control grooves 29, 30, which are connected to the axial bore 36.
  • a further radial bore 55 which rotates in connection with the axial bore 36 is provided in the web 9, so that the same pressure prevails in the control chamber 13 delimited by the control piston sections 4 and 5 as in the axial bore 36.
  • the control chamber 13 is connected via a housing channel 56 to the Control room 57 of the pressure compensator 18 in connection.
  • compression springs 45, 46 are supported by spring plates, which are housed in the end caps 47, 48 and hold the control piston 3 in its shown starting position or middle position.
  • the spaces 49, 50 enclosed by the end caps 47, 48 can be acted upon with control fluid for displacing the control piston against the force of the compression springs 45, 46 in one direction or the other.
  • Axially adjustable stops 51, 52 for the measuring pistons 39, 40 are arranged on the end face of the end cap 47, 48.
  • the measuring pistons have collars 53, 54 on the axial bore side, which are supported on the guide inserts 37, 38 to limit the stroke of the measuring pistons on the stop side. For example, if the space 50 delimited by the end cover 48 is subjected to control pressure, the control piston 3 moves against the force of the compression spring 45 in the direction of the space 49 delimited by the end cover 47.
  • This displacement of the control piston connects the radial bores 42 to the housing recess 20, so that the same pressure prevails in the axial bore 36 of the control piston as in the housing space 20 connected to the consumer connection A via the channel 22.
  • the housing space 20 is connected to the control space 15 via the fine control grooves 29 and with a correspondingly large displacement of the control piston via the control edge 33.
  • the housing seraum 21 communicates with the control chamber 16 connected to the tank via the fine control grooves 31 or the control edge 35.
  • connection channel 1 9 which in this case the counter to the force of the control spring 58 opening pressure compensator 18 and the channel 17 in Control chamber 15 and from there further via the control piston 3 in the open position to the housing recess 20 and further via the channel 22 to the consumer connection A.
  • the working fluid flows via the working line AI to the working chamber Z of the working cylinder V and there displaces the piston K with piston rod St in the direction of the work area Z2.
  • the measuring piston 40 moves so far in the direction of the stop 52 until its collar 54 abuts the annular surface of the guide insert 38.
  • the opposite measuring piston 39 is supported with its end face on the stop 51.
  • This results in a reaction force acting on the control piston 3 in the direction of the control chamber 50, that is to say in the closing direction of the control piston, the size of which is determined by the load or consumer pressure and the active surface of the measuring piston acted on by the load or consumer pressure.
  • the spring force of the compression spring 45 acting on the control piston 3 also acts in the closing direction of the control piston 3.
  • the opening position of the control piston is given control pressure from the prevailing load or consumer pressure.
  • the dimensioning of the cross-sectional area of the volumetric pistons acted upon by the load or consumer pressure must be carried out in such a way that the maximum load or consumer pressure that occurs and the resulting reaction force acting on the control piston additionally the maximum spring force of the compression springs 45 returning the control piston in its central position , 46 is smaller than the control force that can be set on a control unit and acts on the control piston 3 in the opening direction and the cross-sectional area of the control piston on the control pressure.
  • the compression spring loading the control piston in the closing direction also having to be taken into account.
  • the control piston is displaced in the opposite direction by acting on the space 49 delimited by the end cover 47 with control pressure by a control device (not shown), the radial bores 43 connect the axial bore 36 to the housing recess 21, which in this control position of the control piston via the fine control grooves 30 or control edge 34 communicates with the control chamber 15 connected to the pump.
  • the radial bores 42 are kept closed by the guide bore 2 for the control piston 3.
  • the housing recess 20 connected to the working line connection A is connected via the fine control grooves 28 or control edge 32 to the control chamber 14 connected to the tank.
  • the measuring piston 40 In this control position of the control piston, the measuring piston 40 is supported with its end face on the stop 52, while the measuring piston 39 is supported with its collar 53 on the guide insert 37, so that a reaction force resulting from the load or consumer pressure in the closing direction of the control piston, thus occurs in the direction of space 49.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne un dispositif de commande hydraulique comportant au moins un piston de commande pour commander au moins un consommateur, ainsi qu'une source de fluide hydraulique formée par une pompe. La pression de charge intervenant au niveau des consommateurs sert de signal de commande pour piloter le volume de fluide de travail à acheminer jusqu'aux consommateurs et qui est déterminé par la position du piston de commande. Il est prévu, au moins à une extrémité du piston de commande, une chambre de commande sollicitée par la pression de charge, et qui reçoit un piston de mesure guidé vers l'extérieur, dont l'extrémité extérieure peut s'appuyer sur une butée du boîtier. La force résultant de la sollicitation en pression de charge du piston de mesure est dirigée à l'encontre de la force d'amorçage pour déplacer le piston de mesure dans une position d'ouverture déterminant le volume de fluide de travail à acheminer de la source de fluide hydraulique au consommateur. Ce dispositif de commande hydraulique se caractérise en ce que le piston de commande (3) présente une section (9) qui forme conjointement avec l'alésage (2) du boîtier recevant le piston de commande, une chambre de commande (13) qui est reliée par l'intermédiaire d'un alésage transversal (55) à l'alésage axial (36) qui reçoit le piston de mesure (39, 40) formant une chambre de commande, recevant le piston de mesure (39, 40) et guidant la pression de charge ou de consommateur. Un canal (56) du boîtier mène de la chambre de commande (57) vers l'extérieur pour poursuivre l'acheminement de la pression de charge ou de consommateur jusqu'au dispositif d'ajustement d'une pompe à cylindrée variable (P) ou jusqu'à la chambre de commande (57) d'une balance de pression (18) associée au piston de commande (3).
PCT/EP1997/003031 1996-08-07 1997-06-11 Dispositif de commande hydraulique WO1998005870A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19631803.3 1996-08-07
DE19631803A DE19631803B4 (de) 1996-08-07 1996-08-07 Hydraulische Steuervorrichtung

Publications (1)

Publication Number Publication Date
WO1998005870A1 true WO1998005870A1 (fr) 1998-02-12

Family

ID=7801978

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1997/003031 WO1998005870A1 (fr) 1996-08-07 1997-06-11 Dispositif de commande hydraulique

Country Status (2)

Country Link
DE (1) DE19631803B4 (fr)
WO (1) WO1998005870A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10041168A1 (de) * 2000-08-21 2002-03-07 Mannesmann Rexroth Ag Ventileinrichtung
DE102009021103A1 (de) * 2009-05-13 2010-11-18 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
DE102013021317A1 (de) 2013-12-16 2015-06-18 Hydac Filtertechnik Gmbh Hydraulische Ventileinrichtung
DE102022203579A1 (de) 2022-04-08 2023-10-12 Zf Friedrichshafen Ag Vorsteuerbares Druckregelventil und Hydrauliksystem eines Automatgetriebes mit einem vorsteuerbaren Druckregelventil

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3600936B2 (ja) * 1997-04-02 2004-12-15 フォイト トゥルボ ゲーエムベーハー ウント コンパニー コマンディトゲゼルシャフト バルブ装置、特に比例バルブ兼方向制御バルブ
DE10121924A1 (de) 2001-05-05 2002-11-07 Bosch Rexroth Ag Hydraulische Steueranordnung zur Steuerung eines einfachwirkenden hydraulischen Verbrauchers hinsichtlich Richtung und Geschwindigkeit und Wegeventil dafür
DE10245836B4 (de) * 2002-04-26 2013-03-14 Bosch Rexroth Aktiengesellschaft LS-Wegeventilanordnung
EP2918853B1 (fr) * 2014-03-11 2016-03-09 Bucher Hydraulics S.p.A. Section hydraulique pour des applications de détection de charge et de multiples distributeurs hydrauliques
DE102022202288A1 (de) 2022-03-08 2023-09-14 Robert Bosch Gesellschaft mit beschränkter Haftung Arbeitsvorrichtung mit einem Ventil, welches wenigstens eine gesonderte Entleerstellung hat
DE102022204640A1 (de) 2022-05-12 2023-11-16 Robert Bosch Gesellschaft mit beschränkter Haftung Ventilanordnung für den Frontlader eines landwirtschaftlichen Traktors
DE102022208305A1 (de) 2022-08-10 2024-02-15 Robert Bosch Gesellschaft mit beschränkter Haftung Druckwaagenanordnung mit Lasthaltung und Flow-Boost
DE102022208306A1 (de) 2022-08-10 2024-02-15 Robert Bosch Gesellschaft mit beschränkter Haftung Druckwaagenanordnung mit Flow-Cut-Funktion

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2236132A1 (fr) * 1973-07-03 1975-01-31 Messier Hispano Sa
EP0052709A1 (fr) * 1980-11-26 1982-06-02 Robert Bosch Gmbh Distributeur
US4407122A (en) * 1981-05-18 1983-10-04 Vickers, Incorporated Power transmission
DE3622925A1 (de) * 1985-07-10 1987-01-15 Linde Ag Kombiniertes umschalt- und druckbegrenzungsventil
EP0331958A2 (fr) * 1988-03-08 1989-09-13 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Dispositif de commande hydraulique

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4234037C2 (de) * 1992-10-09 2001-03-22 Mannesmann Rexroth Ag Ventilanordnung, insbesondere für mobile Arbeitsgeräte
GB2277066B (en) * 1993-03-24 1996-02-28 Ultra Hydraulics Ltd Hydraulic flow control valve assemblies
SE501289C2 (sv) * 1993-06-24 1995-01-09 Voac Hydraulics Boraas Ab Styrorgan för en hydraulisk motor
DE29515829U1 (de) * 1995-10-05 1995-11-30 Heilmeier & Weinlein Hydraulische Steuervorrichtung und Zweiwege-Regelventil

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2236132A1 (fr) * 1973-07-03 1975-01-31 Messier Hispano Sa
EP0052709A1 (fr) * 1980-11-26 1982-06-02 Robert Bosch Gmbh Distributeur
US4407122A (en) * 1981-05-18 1983-10-04 Vickers, Incorporated Power transmission
DE3622925A1 (de) * 1985-07-10 1987-01-15 Linde Ag Kombiniertes umschalt- und druckbegrenzungsventil
EP0331958A2 (fr) * 1988-03-08 1989-09-13 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Dispositif de commande hydraulique

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10041168A1 (de) * 2000-08-21 2002-03-07 Mannesmann Rexroth Ag Ventileinrichtung
DE102009021103A1 (de) * 2009-05-13 2010-11-18 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
DE102013021317A1 (de) 2013-12-16 2015-06-18 Hydac Filtertechnik Gmbh Hydraulische Ventileinrichtung
WO2015090493A1 (fr) 2013-12-16 2015-06-25 Hydac Filtertechnik Gmbh Dispositif à soupape hydraulique
US9791065B2 (en) 2013-12-16 2017-10-17 Hydac Filtertechnik Gmbh Hydraulic valve device
DE102022203579A1 (de) 2022-04-08 2023-10-12 Zf Friedrichshafen Ag Vorsteuerbares Druckregelventil und Hydrauliksystem eines Automatgetriebes mit einem vorsteuerbaren Druckregelventil

Also Published As

Publication number Publication date
DE19631803A1 (de) 1998-02-12
DE19631803B4 (de) 2007-08-02

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