EP0901577A1 - Dispositif hydraulique de commande pilote actionne manuellement - Google Patents

Dispositif hydraulique de commande pilote actionne manuellement

Info

Publication number
EP0901577A1
EP0901577A1 EP97927118A EP97927118A EP0901577A1 EP 0901577 A1 EP0901577 A1 EP 0901577A1 EP 97927118 A EP97927118 A EP 97927118A EP 97927118 A EP97927118 A EP 97927118A EP 0901577 A1 EP0901577 A1 EP 0901577A1
Authority
EP
European Patent Office
Prior art keywords
control
spring
housing
piston
sleeve
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
EP97927118A
Other languages
German (de)
English (en)
Other versions
EP0901577B1 (fr
Inventor
Peter BÜTTNER
Lucia Jelitte
Konrad Stahl
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.)
Bosch Rexroth AG
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 EP0901577A1 publication Critical patent/EP0901577A1/fr
Application granted granted Critical
Publication of EP0901577B1 publication Critical patent/EP0901577B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/0422—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with manually-operated pilot valves, e.g. joysticks
    • 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
    • Y10T137/87056—With selective motion for plural valve actuator
    • Y10T137/87064—Oppositely movable cam surfaces

Definitions

  • the invention is based on a manually operated hydraulic pilot control device which has the features from the preamble of claim 1, which corresponds to the preamble of the independent claim 7.
  • Such a manually operated hydraulic pilot control device is known for example from DE 27 51 946 C2. It works on the basis of continuously adjustable pressure reducing valves, at the control output of which a pilot pressure dependent on the deflection of a hand lever can be set.
  • the hydraulic pilot control device shown in the cited document has a continuous housing bore in a housing, which has a control section in the interior of the housing in which the control piston of a pressure reducing valve is guided so as to be axially displaceable in a tight manner. Bore sections with a larger diameter are connected on both sides of the control section.
  • a guide bush is screwed into one end of the housing bore, in which a plunger is axially displaceably guided, which protrudes in the direction away from the housing over the guide bush and can strike the guide bush with a collar at its inner end. At its end projecting outwards over the guide bushing, the tappet can be acted upon by a hand lever via an intermediate member.
  • a spring plate is pressed inside the plunger by two helical compression springs.
  • One helical compression spring is a return spring for the plunger and for the hand lever and is supported on the shoulder plate of the housing bore, which limits its control section in one direction, in addition to the spring plate.
  • the second compression spring is the regulating spring of the pressure reducing valve, which is supported on a shoulder of the regulating piston in addition to the spring plate, which means that it can act in a direction away from the tappet.
  • the control piston extends through the control spring with a long neck and engages behind the spring plate on the tappet with a head. When the head rests on the spring plate, there is a free space in the axial direction between the head and the plunger, which allows a relative displacement between the control piston and the plunger.
  • the control piston is a hollow piston with an axial blind bore, which on the end of the control piston facing away from the tappet is open to a section of the housing bore which is in the form of a screw connection and which represents the control output of the pressure reducing valve.
  • Several radial bores run between the blind bore and the outside of the control piston, via which, depending on the position of the control piston Space in which the return spring and the control spring are located and which is connected to a tank outlet of the pilot control device, or a control room which is connected to the pressure input of the pilot control device, can be connected to the blind bore and thus to the control output.
  • the spring chamber containing the return spring and the control spring and the control chamber are separated from one another by a narrow housing web, the axial extent of which is slightly larger than the diameter of the radial bores in the control piston.
  • the control piston is in the control position when the radial bores are at least almost completely covered by the housing web. In this control position, there is a balance between the axially directed forces acting on the control piston.
  • the force acting in one direction by the control spring is the same as the counterforce generated by the pressure at the control outlet on the cross-sectional area of the control piston.
  • Small movements of the control piston out of the control position connect the blind bore and thus the control outlet with the tank outlet or the pressure inlet, whereby the pressure in the control outlet is kept largely constant in a certain position of the tappet.
  • the radial bores in the control piston are at a distance from the control chamber connected to the pressure input.
  • the control spring is clamped between the control piston and the plunger with a certain preload force.
  • a pilot control pressure can be set in accordance with the control curve shown in FIG. 2 depending on the deflection of the hand lever or the stroke of the tappet.
  • the control piston is carried along by the plunger via the control spring and the spring plate on the plunger, without pressure initially building up in the control outlet. This free travel is determined by the initial distance between the radial bores in the control piston and the control chamber connected to the pressure input of the pilot control device.
  • the control pressure jumps to a value which is determined by the biasing force of the control spring in the zero position.
  • control spring With a further deflection of the hand lever and a further displacement of the tappet, the control spring is compressed further, while the control piston remains in the area of its control position or returns to its control position after the corresponding pressure in the control outlet has built up.
  • the control pressure increases linearly with the tappet stroke.
  • the level of the pressure jump at the end of the free travel and a response threshold of the hydraulic main unit, which is controlled with the pilot control unit, for example the response threshold of an actuating cylinder for the adjustment of a variable displacement pump, are coordinated. If the pressure jump on the pilot control device is lower than the threshold on the main device, the lever or tappet travel on the pilot control device increases until the main device responds. This is noticeable in an enlargement of the free travel and in a speed difference-controlled steering as increased steering play. If the initial jump in pressure is higher than the response threshold of the main unit, the pilot control becomes less sensitive.
  • the aim of the invention is to further develop a manually operated hydraulic pilot control device which has the features from the preamble of claim 1 and claim 8, respectively, in such a way that the free travel can be adjusted in a simple manner.
  • control piston is displaceable in a control sleeve introduced into the housing bore and that the axial position of the control sleeve is adjustable from the second open end of the housing bore.
  • the control edges formed on the control sleeve and interacting with the control piston can be displaced within the housing bore and can be brought into such a position that a flow cross-section between the .multidot Control output and the pressure input is opened.
  • the accessibility of the control sleeve from the second open end of the housing bore makes the adjustment particularly simple since no parts of the 4th
  • Pilot device is necessary to get to the control sleeve.
  • the aim of the invention is also to further develop a manually operated hydraulic pilot control device which has the features from the preamble of claim 1 and claim 8, respectively, in such a way that the amount of the initial jump can be set in the control pressure.
  • this additional adjusting spring is at least approximately always equally tensioned, so that a constant force is added to the force exerted by the control spring on the control piston, taking into account the direction of force.
  • the initial jump in the control pressure can be increased or decreased.
  • the adjustable stop fixed to the housing can easily be arranged so that it is accessible from the outside. This makes adjustment particularly easy.
  • control sleeve can advantageously be installed in the housing bore from the second open end thereof. As a result, no changes to known pilot control devices are necessary in the area of the tappet.
  • the control sleeve is preferably screwed into the housing and has an external polygon for attaching a screwing tool. If a restoring spring acting on the tappet is supported on the control sleeve, no support shoulder in the housing bore is necessary. The change in the preload of the return spring the position of the control sleeve is only slight and is hardly noticeable when the pilot control device is actuated.
  • a shoulder is formed in the housing bore, against which the control sleeve can be placed during installation in the housing. This establishes a starting point in which the distance between the control edges on the control sleeve and control piston controlling the flow cross-section between the pressure inlet and the control outlet is extreme and from which the distance can be adjusted by moving the control sleeve back.
  • Claim 7 specifies how control oil can be advantageously fed to the control output and removed from the control output.
  • the control output is not in the axis of the control piston, since a control line connected to the control sleeve could prevent the adjustment, in particular the rotation of the control sleeve.
  • the pilot control device is particularly preferably developed according to claim 11. According to this claim, there is a spring chamber on both sides of a control bore in which a control section of the control piston is guided.
  • the control spring and possibly a restoring spring acting on the tappet are accommodated by the one, first spring space, while the adjusting spring is located in the other, second spring space, that is to say opposite the control spring with respect to the control section on the control piston.
  • the construction of the pilot control device becomes particularly simple if the adjusting spring acts on the control piston as a compression spring in the opposite direction to the control spring. The force of the adjusting spring is therefore added to the pressure force opposing the force of the control spring.
  • the second spring chamber is connected to the control output. This is advantageously done by a radial outlet from the second spring chamber, because an axial outlet and a control line connected in the axis of the control piston would hinder the adjustment of the stop for the adjusting spring.
  • a pilot control device according to claim 15, according to which an adjustable housing-fixed stop for the adjusting spring and a control sleeve which is introduced into the housing bore and adjustable in its axial position without the need for of excessive space are combined with each other, so that free travel and pressure jump height can be set very precisely.
  • the free travel is adjusted by moving the control sleeve and then the preload of the adjusting spring is adjusted by moving the stop.
  • FIG. 1 shows a longitudinal section through the embodiment and FIG. 2 shows the control curve.
  • the exemplary embodiment of a pilot control device which operates on the basis of one or more pressure reducing valves 9, has a housing 10 with a continuous housing bore 11 with sections of different diameters.
  • a guide bushing 12 is screwed into the housing bore 11 from one end into the housing bore 11 to such an extent that it rests on the housing 10 with an outer shoulder 13.
  • a plunger 14 is axially guided in the guide bushing 12, which can be pressed with a collar 15 against the inwardly facing end face of the guide bushing 12 and which has a blind bore 16 which is open into the interior of the housing bore 11.
  • the plunger 14 projects beyond the guide bush 12 by a distance which is greater than the necessary axial displacement path.
  • the tappet 14 can be actuated via a pivotable hand lever (not shown in more detail).
  • control sleeve 20 is screwed into it, on the outside of which one can distinguish essentially four sections lying axially one behind the other.
  • the control sleeve 20 has an external hexagon 21, on which a screwing tool can be attached to turn the control sleeve.
  • the external hexagon 21 is followed by a threaded section 22, the external thread of which engages in an internal thread in the housing bore 11. This is followed by three circular-cylindrical sections 23, 24 and 25, the section 23 adjoining the threaded section 22 having the largest outside diameter, the following section 24 having an average outside diameter and the last section 25 having the smallest outside diameter.
  • annular space 27 is formed between the sleeve section 25 and the housing 10 and an annular space 28 is formed between the sleeve section 24 and the housing 10.
  • the bore section 36 extends axially over the sleeve section 25 and over approximately two thirds of the sleeve section 24. It serves as a guide bore for the control piston 50 and as a control bore for the entire pressure reducing valve 9 shown and controls it together with the control piston 50 Connections between the different connections of the valve. It has an annular control space 38 which is separated from a spring space 39 located in front of the sleeve section 25 by a web 40 of the control sleeve. The ring edges between the end faces of the web 40 and the bore section 36 form the stationary control edges 41 and 42 of the pressure reducing valve 9.
  • the control chamber 38 is connected to the ring chamber 27 via a plurality of radial bores 43.
  • the bore section 37 has a larger diameter than the bore section 36 and is connected to the annular space 28 via a plurality of radial bores. It is closed to the outside by an adjusting screw 45 with a hexagon socket 46, which is screwed into the control sleeve 20 and secured in position by a lock nut 47. A locking ring 48 inserted into the control sleeve 20 limits the adjustment path of the adjustment screw 45 to the outside.
  • the control piston 50 is a hollow piston with an axial blind bore 51, which is open to the bore section 37 of the control sleeve 20 and is connected to the outside of the control piston via a plurality of radial bores 52.
  • the diameter of the radial bores 52 is slightly smaller than the axial distance between the two control edges 41 and 42 on the control sleeve 20, so that the radial bores can be completely covered by the web 40.
  • the control piston 50 extends through the spring chamber 39 with a neck 53 and projects with a head 54 into the blind bore 16 of the plunger 14. With its head 54 it engages behind a disk 55 which is arranged between the collar 15 of the plunger 14 and a spring plate 56 and which holds the head 54 in the manner of a slotted locking ring.
  • a return spring 60 received by the spring chamber 39 is supported on the one hand on the control sleeve 20 and on the other hand via the spring plate 56 and the disk 55 on the tappet 14, which it presses against the guide bush 12 in the rest position of the pressure reducing valve 9. Furthermore, a control spring 61 is opened from the spring chamber 39. are taken, which is clamped between a shoulder 59 of the control piston 50 and the spring plate 56 and which ensures that the head 54 of the control piston 50 rests on the disk 55 in the rest position of the plunger 14.
  • the free area of the bore section 37 between the control sleeve 20 and the adjusting screw 45 accommodates an adjusting spring 62 as spring space 67, which is clamped between the adjusting screw 45 and a spring plate 63, which has a continuous axial bore 64, with a Collar 65 abuts the control piston 50 and is guided in the control piston 50 on the one hand and even guides the adjusting spring 62.
  • the spring chamber 39 is connected via a channel 70 to a tank outlet T, the annular chamber 27 via a channel 71 to a pressure inlet P and the annular chamber 28 via a channel 72 to a control outlet A of the pressure reducing valve 9.
  • the control sleeve 20 is secured by a locking screw, not shown, screwed into a radial threaded bore 66.
  • the control sleeve 20 is screwed into the housing 10 up to a stop.
  • the radial bores 52 are at a certain clear distance from the control edge 42.
  • Tolerances of the housing 10, the guide sleeve 12 and the tappet 14, the control sleeve 20 and the regulating piston 50 go into the distance between the control edge 42 and the radial bores 52.
  • a desired distance between the control edge 42 and the radial bores 52 can now be adjusted independently of the tolerances.
  • the desired height of the pressure jump after the free travel a can be set within certain limits.
  • the setting range is given in FIG. 2 by the vertical distance between the two obliquely rising dashed lines.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Fluid Pressure (AREA)
  • Servomotors (AREA)

Abstract

L'invention concerne un appareil hydraulique de commande pilote actionné manuellement muni d'une soupape de réduction de pression (9) ajustable en continu, comprenant un boîtier (10) et un piston de régulation (50) situé dans un alésage (11) traversant du boîtier. Ledit piston de régulation (50) peut être sollicité par un ressort de régulation (61) pour qu'une entrée de pression (P) communique avec une sortie de régulation (A) et peut être sollicité par une pression appliquée dans la sortie de régulation (A) pour empêcher cette communication. Le ressort de régulation (61) est monté entre une première butée (59) fixe du piston de régulation (50) et une coupelle (56) pouvant être appliquée sur une seconde butée (54) fixe du piston de régulation (50) et pouvant être entraînée par une tige-poussoir (14) guidée dans le sens axial et située sur la première extrémité ouverte de l'alésage (11) du boîtier, et pouvant être soutenue à distance de la seconde butée (54) du piston de régulation (50). Afin de pouvoir ajuster la course à vide jusqu'à la variation brusque initiale de la pression de régulation, le piston de régulation (50) peut être déplacé dans un manchon de commande (20) introduit dans l'alésage (11) du boîtier, dont la position axiale peut être ajustée depuis la seconde extrémité ouverte de l'alésage (11) du boîtier. L'amplitude de la variation brusque de la pression peut être ajustée du fait qu'un ressort d'ajustement (62) est monté entre le piston de régulation (50) et une butée (45) ajustable solidaire du boîtier.
EP97927118A 1996-06-07 1997-06-03 Dispositif hydraulique de commande pilote actionne manuellement Expired - Lifetime EP0901577B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19622948 1996-06-07
DE19622948A DE19622948C2 (de) 1996-06-07 1996-06-07 Manuell betätigbares hydraulisches Vorsteuergerät
PCT/EP1997/002876 WO1997047890A1 (fr) 1996-06-07 1997-06-03 Dispositif hydraulique de commande pilote actionne manuellement

Publications (2)

Publication Number Publication Date
EP0901577A1 true EP0901577A1 (fr) 1999-03-17
EP0901577B1 EP0901577B1 (fr) 2002-10-30

Family

ID=7796428

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97927118A Expired - Lifetime EP0901577B1 (fr) 1996-06-07 1997-06-03 Dispositif hydraulique de commande pilote actionne manuellement

Country Status (5)

Country Link
US (1) US6152179A (fr)
EP (1) EP0901577B1 (fr)
JP (1) JP2000512366A (fr)
DE (2) DE19622948C2 (fr)
WO (1) WO1997047890A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2187719C1 (ru) * 2001-05-31 2002-08-20 Шпак Леонид Семенович Устройство для регулирования подачи жидкости
FR2857706B1 (fr) * 2003-07-17 2007-05-04 Bosch Rexroth Dsi Sas Dispositif distributeur de fluide sous pression a double ressorts de regulation
ITMO20040064A1 (it) * 2004-03-26 2004-06-26 Salami Spa Dispositivo di comando a mezzo fluido
ITMO20050247A1 (it) * 2005-09-29 2007-03-30 Studio Tecnico 6M Srl Valvola per la frenatura idraulica di macchine operatrici o simili
DE102008037981B4 (de) * 2007-10-02 2023-01-26 Continental Automotive Technologies GmbH Schieberventil
CN101532527B (zh) * 2009-04-22 2011-04-13 黄培华 调压控制气阀
DE102010006196A1 (de) 2010-01-29 2011-08-04 Robert Bosch GmbH, 70469 Hydraulisches Vorsteuergerät
CN102878133A (zh) * 2011-07-12 2013-01-16 上海立新液压有限公司 恒压控制阀
DE102019218402B4 (de) * 2019-11-27 2022-09-22 Hawe Hydraulik Se Federdom für ein Hydraulikventil und Hydraulikventil mit einem solchen Federdom

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US3599675A (en) * 1970-02-06 1971-08-17 Ato Inc Proportional valve
DE2152133B1 (de) * 1971-10-20 1973-02-22 Rexroth Gmbh G L Hydraulisch betaetigtes steuerventil
NO143570C (no) * 1975-05-20 1981-03-11 Hydraulik Brattvaag As Anordning ved fjernstyrt manoeverventil.
FR2376978A1 (fr) * 1977-01-06 1978-08-04 Rexroth Sigma Perfectionnements aux dispositifs distributeurs de fluide, notamment pour telecommande hydraulique
US4342335A (en) * 1980-10-23 1982-08-03 Koehring Company Hydraulic valve detent mechanism
DE3321972A1 (de) * 1982-06-24 1983-12-29 Thyssen Industrie Ag, 4300 Essen Ventil zur steuerung von fluidem, insbesondere hydraulischem druckmittel vornehmlich fuer schubkolbengetriebe von ausbauelementen des untertaegigen grubenbetriebes
DE3635625A1 (de) * 1986-10-20 1988-04-28 Rexroth Mannesmann Gmbh Vorsteuergeraet
US4819695A (en) * 1987-06-19 1989-04-11 Bendix France Pressure servo regulator
DE8716781U1 (de) * 1987-12-21 1989-05-11 Robert Bosch Gmbh, 7000 Stuttgart Proportional arbeitendes Druckbegrenzungsventil
DE8806210U1 (de) * 1988-05-10 1988-07-07 MBK-Hydraulik Meuwsen & Brockhausen GmbH & Co KG, 4132 Kamp-Lintfort Hydrauliksteuerung für unter Tage
DE4011593C2 (de) * 1990-04-10 1995-11-30 Rexroth Mannesmann Gmbh Einstellbares Druckventil
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US5482085A (en) * 1992-10-05 1996-01-09 Dana Corporation Pilot pressure sub-assembly for fluid control valve

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Title
See references of WO9747890A1 *

Also Published As

Publication number Publication date
WO1997047890A1 (fr) 1997-12-18
DE59708624D1 (de) 2002-12-05
EP0901577B1 (fr) 2002-10-30
DE19622948A1 (de) 1997-12-11
DE19622948C2 (de) 2001-08-02
JP2000512366A (ja) 2000-09-19
US6152179A (en) 2000-11-28

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