WO1991019108A1 - Equipement de commande pour un cylindre de travail - Google Patents

Equipement de commande pour un cylindre de travail Download PDF

Info

Publication number
WO1991019108A1
WO1991019108A1 PCT/DE1991/000372 DE9100372W WO9119108A1 WO 1991019108 A1 WO1991019108 A1 WO 1991019108A1 DE 9100372 W DE9100372 W DE 9100372W WO 9119108 A1 WO9119108 A1 WO 9119108A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
directional
directional control
piston
control valve
Prior art date
Application number
PCT/DE1991/000372
Other languages
German (de)
English (en)
Inventor
Günther Schwerin
Walter Gerschwitz
Hans Aichele
Friedrich-Wilhelm Höfer
Günter DRIEDGER
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
Priority to JP91507690A priority Critical patent/JPH05507138A/ja
Publication of WO1991019108A1 publication Critical patent/WO1991019108A1/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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/26—Locking mechanisms
    • F15B15/262—Locking mechanisms using friction, e.g. brake pads
    • 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
    • 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

Definitions

  • the invention relates to a control device according to the type of the main claim.
  • a control device according to the type of the main claim With such a known device according to DE-OS 38 16 509 there are difficulties with regard to the construction of the directional control valve, and the positioning and locking of the piston rod also present certain difficulties.
  • control device with the characterizing features of the main claim has the advantage that the control of the working cylinder is reliable and reliable locking of the piston rod is guaranteed.
  • FIGS. 1 and 2 Two embodiments of the invention are shown in the following description and drawing.
  • the latter shows, in FIGS. 1 and 2, two exemplary embodiments of hydraulic control devices in a schematic representation. Description of the invention example
  • 10 represents a double-acting cylinder, the two pressure chambers are designated 11, 12.
  • the position of the piston 13 is detected with the aid of a displacement sensor 14 on a piston rod 13A and is signaled to an electronic control system 16 via an electrical line 15.
  • the working cylinder 10 is controlled by a 4/3-way valve 17, which is actuated with the aid of a double-stroke proportional electromagnet 18, which in turn is controlled by the electronic control unit 16 via electrical lines 19, 20.
  • the directional control valve 17 is centered in neutral position II by two springs 21, 22.
  • Two lines 23, 24 are connected to the directional control valve 17, each of which is connected to a check valve 25 or 25A, both of which have the same design and whose valve bodies 27 and 27A each have plungers 28 and 28A provided with tappets 26 and 26A be operated. Compression springs 29, 30 and 29A, 30A act on the push-open pistons 28 and 28A and the valve bodies 27 and 27A in opposite directions.
  • the check valves 25 and 25A are actuated by two control lines 31, 32 which are connected to a line 33. This line 33 is connected to a 3/2-way valve 34 which is actuated by an electromagnet 35 which is controlled by the electronic control system 16 via an electrical line 36.
  • the 3/2-way valve is centered in neutral position I by means of a spring 37.
  • a line 38 in which a throttle 39 and a check valve 40 are arranged, leads from the opposite connection side of the 3/2-way valve 34 to a pressure medium source 41, in particular a pressure accumulator, which is charged by a pump (not shown).
  • Another line 42 leads from the same connection side of the 3/2-way valve 34 to a container 43.
  • Lines 44, 45 open into the pressure chambers 11, 12 of the working cylinder 10 and are each connected to the check valves 25 and 25A in such a way that they are connected to the lines 23, 24 when the check valves are open.
  • a mechanical brake 46 which is actuated by a spring 47, acts on the piston rod 13A of the working cylinder 10.
  • the mechanical brake 46 is raised against the spring action by a cylinder 48, which is also connected to the line 33 by a line 49.
  • a leak oil line 70 leads from the cylinder 48 via the return line 50 to the return line 42.
  • the directional control valve 17 is also connected to the return line 50 via a return line 51, in which a throttle 52 is attached.
  • the directional control valve 17 is connected to the line 33 via a line 53 in which a throttle 54 is arranged.
  • the working cylinder 10 is hydraulically locked in the switching position of the directional control valve 34 shown, since both check valves 25, 25A are closed by the connection of their control lines 31, 32 to the container 43. At the same time, the working cylinder 10 is mechanically locked, since the cylinder 48 of the brake 46 is also connected to the container 43 via the line 49. In addition, the directional control valve 17 is cut off from the pressure supply 41 - that is to say without pressure.
  • the directional control valve 17 is switched to switch position III when the 3/2-way valve 34 is already in switch position II. Pressure medium thus reaches the cylinder 48 of the braking device 46 via the lines 33 and 49, which is lifted off the piston rod 13A. At the same time, the check valves 25 and 25A are opened via the control lines 31, 32, so that the pressure chambers 11, 12 of the Working cylinder 10 are connected to the directional control valve 17. In switch position III of the directional control valve 17, the pressure chamber 12 is thereby supplied with pressure medium, while at the same time the pressure chamber 11 is connected to the container 43 via the line 23 and the directional control valve 17 as well as the lines 51, 50, 42.
  • FIG. 2 shows a further exemplary embodiment which, in addition to the one shown in FIG. 1, contains a 4/3-way valve 55 which is actuated via a double-stroke electric switching magnet 56, which in turn is supplied by electrical lines 57, 58 from the electronic control unit 16 is controlled.
  • This valve is centered in its neutral position II by two compression springs 59, 60.
  • the spring 60 the spring force of which is greater than that of the spring 59, abuts a stop 62 with an end plate 61 in the neutral position II of the valve 55 and thus ensures a safe setting of the neutral position II of the valve 55.
  • the 4/3-way valve 55 is connected to the return line 42 via a return line 63.
  • a second connection 64 on this side of the directional control valve 55 connects it to the line 33.
  • the line 49 leads to the cylinder 48 of the brake 46, so that it has no direct connection to the line 33.
  • the line 53 on the directional control valve 17 is also connected to the 4/3-way valve 55 on this connection side, so that this likewise has no direct connection to the line 33.
  • switch position I the 4/3-way valve 55 connects the lines 53 and 49 to the line 33, so that the movements of the working cylinder 10 are controlled analogously to the embodiment shown in FIG.
  • the 4/3-way valve 55 connects the line 53 to the line 33 and the line 49 to the return line 63. This makes it possible to test the function of the brake, since it is relieved of pressure and is therefore pressed against the piston rod 13A while simultaneously one of the two pressure chambers 11, 12 of the working cylinder 10 can be supplied with pressure medium via the directional control valve 17.
  • check valves 25, 25A are not influenced by the 4/3-way valve 55, so that these check valves remain functional even if, for example, the pressure from the line 49 cannot be removed (the braking device 46 would then not work) .

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

Dans le cas d'un cylindre de travail à double effet (10), les mouvements du piston sont transmis par l'intermédiaire d'un palpeur de position (14) à un système de commande électronique (16). Un frein mécanique (46) agit sur la tige de piston (13A). Les chambres de pression (11, 12) du cylindre de travail sont reliées par l'intermédiaire de soupapes d'arrêt (25, 25A) à une soupape à 4/3 voies (17). La soupape à 4/3 voies (17), les soupapes d'arrêt (25, 25A) et les cylindres de travail (48) du frein (46ç) sont reliés par l'intermédiaire d'une soupape à 3/2 voies (34) à une source de fluide sous pression (41). Les soupapes à voies sont sélectionnées par le système de commande électronique (16).
PCT/DE1991/000372 1990-05-26 1991-05-04 Equipement de commande pour un cylindre de travail WO1991019108A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP91507690A JPH05507138A (ja) 1990-05-26 1991-05-04 作業シリンダのための制御装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9005983U DE9005983U1 (fr) 1990-05-26 1990-05-26
DEG9005983.2.U 1990-05-26

Publications (1)

Publication Number Publication Date
WO1991019108A1 true WO1991019108A1 (fr) 1991-12-12

Family

ID=6854147

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1991/000372 WO1991019108A1 (fr) 1990-05-26 1991-05-04 Equipement de commande pour un cylindre de travail

Country Status (4)

Country Link
EP (1) EP0531304A1 (fr)
JP (1) JPH05507138A (fr)
DE (1) DE9005983U1 (fr)
WO (1) WO1991019108A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2270778A (en) * 1992-09-17 1994-03-23 Rexroth Mannesmann Gmbh Circuit for a servo-hydraulic regulating system
EP0756089A3 (fr) * 1993-04-05 1998-03-25 Deere & Company Système hydraulique de contrÔle
WO1998013627A1 (fr) * 1996-09-27 1998-04-02 Kongsberg Automotive Asa Dispositif pour fluide sous pression
US8671986B2 (en) 2007-06-05 2014-03-18 Sanyo Kiki Co., Ltd. Hydraulic controller

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010054108A1 (de) * 2010-12-10 2012-06-14 Hydac System Gmbh Ventilanordnung zur Steuerung eines Zusatz-Lenksystems bei mehrachsigen Fahrzeugen, insbesondere Mobilkranen

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3498182A (en) * 1968-05-07 1970-03-03 Sheffer Corp The Locking cylinder
FR2129871A1 (fr) * 1971-03-17 1972-11-03 Poclain Sa
US3908515A (en) * 1973-09-10 1975-09-30 Caterpillar Tractor Co Hydraulic circuit with selectively actuatable float control
DE3736750A1 (de) * 1987-10-30 1989-05-11 Schneider Co Optische Werke Elektrohydraulischer oder elektropneumatischer linear-stellantrieb

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3498182A (en) * 1968-05-07 1970-03-03 Sheffer Corp The Locking cylinder
FR2129871A1 (fr) * 1971-03-17 1972-11-03 Poclain Sa
US3908515A (en) * 1973-09-10 1975-09-30 Caterpillar Tractor Co Hydraulic circuit with selectively actuatable float control
DE3736750A1 (de) * 1987-10-30 1989-05-11 Schneider Co Optische Werke Elektrohydraulischer oder elektropneumatischer linear-stellantrieb

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2270778A (en) * 1992-09-17 1994-03-23 Rexroth Mannesmann Gmbh Circuit for a servo-hydraulic regulating system
GB2270778B (en) * 1992-09-17 1996-01-03 Rexroth Mannesmann Gmbh Circuit for a servo-hydraulic regulating system
US5490442A (en) * 1992-09-17 1996-02-13 Mannesmann Rexroth Gmbh Safety circuit for a servo-hydraulic regulating system
EP0756089A3 (fr) * 1993-04-05 1998-03-25 Deere & Company Système hydraulique de contrÔle
WO1998013627A1 (fr) * 1996-09-27 1998-04-02 Kongsberg Automotive Asa Dispositif pour fluide sous pression
US6223533B1 (en) 1996-09-27 2001-05-01 Kongsberg Automotive Asa Pressurized fluid device
US8671986B2 (en) 2007-06-05 2014-03-18 Sanyo Kiki Co., Ltd. Hydraulic controller

Also Published As

Publication number Publication date
EP0531304A1 (fr) 1993-03-17
DE9005983U1 (fr) 1991-09-19
JPH05507138A (ja) 1993-10-14

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