EP0733743A1 - Dispositif pour une distribution du débit de fluide indépendante de la pression de charge des vannes de commande d'engins de chantier - Google Patents

Dispositif pour une distribution du débit de fluide indépendante de la pression de charge des vannes de commande d'engins de chantier Download PDF

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Publication number
EP0733743A1
EP0733743A1 EP96102897A EP96102897A EP0733743A1 EP 0733743 A1 EP0733743 A1 EP 0733743A1 EP 96102897 A EP96102897 A EP 96102897A EP 96102897 A EP96102897 A EP 96102897A EP 0733743 A1 EP0733743 A1 EP 0733743A1
Authority
EP
European Patent Office
Prior art keywords
pressure
consumers
closure element
spring
compensator
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
EP96102897A
Other languages
German (de)
English (en)
Other versions
EP0733743B1 (fr
Inventor
Günther Brönner
Gustav Leidinger
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.)
CNH Industrial Baumaschinen GmbH
Original Assignee
O&K Orenstein and Koppel 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
Priority claimed from DE19520451A external-priority patent/DE19520451C1/de
Application filed by O&K Orenstein and Koppel GmbH filed Critical O&K Orenstein and Koppel GmbH
Publication of EP0733743A1 publication Critical patent/EP0733743A1/fr
Application granted granted Critical
Publication of EP0733743B1 publication Critical patent/EP0733743B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/3054—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and output member
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in control
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6052—Load sensing circuits having valve means between output member and the load sensing circuit using check 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/78—Control of multiple output members

Definitions

  • the invention relates to a device for load pressure independent flow distribution in a spool for mobile construction and work machines.
  • the first-mentioned embodiment is complex, while the latter two are so sensitive to the signal output that a pressure-accurate forwarding of the load-sensing signal is not always guaranteed via the control edges with the small oil flows. This causes inaccurate control of the pump controller, which in turn has a negative impact on the overall control, i.e. the control of individual or multiple consumers affects.
  • the object of the invention is to develop a device for load pressure independent flow distribution in a spool valve for mobile construction and work machines in such a way that there is a cost-effective, simple and trouble-free solution in which the required oil flow is reliably and accurately passed on to the pump controller.
  • a device for load pressure-independent flow distribution in a control slide for mobile construction and work machines which is in operative connection with at least two downstream consumers and which provides the flow rate provided by at least one controllable feed pump according to the load pressure-independent principle via correspondingly controllable piston-type compensators or several of the consumers are available and the highest of the pressures at the consumers is reported to the regulator of the feed pump, the compensators on the one hand containing a pressure chamber that can be connected to the respective consumer and on the other hand a spring chamber that connects consumers to the spring chamber via corresponding channels are and in the connecting line at least one two defined positions taking closure element is inserted.
  • the subject of the invention can be used for any number of consumers which are controlled via a control slide operating on the principle of flow pressure-independent flow distribution.
  • a major advantage of a spherical or conical closure element compared to a piston is that the spherical or conical closure element only knows two defined positions, namely 'open' or 'closed', while when a piston is used, only one occurs due to the constantly changing direction so-called snapping on the control edges, which is ultimately reflected in the unfavorable delivery of the required oil flow.
  • This disadvantage is effectively eliminated by the closure element according to the invention, since it is now possible to deliver a sufficient oil flow to the pump regulator and the additional compensators due to the cross section released by the ball or cone position " open".
  • the single figure shows a schematic diagram of the schematic structure of a control system with any number of consumers; in this example designed as a cylinder 1,2,3.
  • the cylinders 1, 2, 3 are controlled by a control slide, which is constructed according to the principle of flow pressure-independent flow distribution, of which only the control openings 4, 5, 6 are shown. These control openings 4, 5, 6 can be changed by the driver.
  • the compensator 10 designed as a piston, the slide section of which is assigned to the cylinder 1, is activated so that its oil flow can flow to this cylinder 1.
  • the cylinder pressure p z1 which has to serve as an LS signal, is planted via transverse channels 11 in the compensator piston 10 by lifting the spherical closure element 12 via the line 13, on which the other compensator pistons 14, 15 are also connected in parallel , to pump controller 8.
  • the spherical closure element 12 via the line 13, on which the other compensator pistons 14, 15 are also connected in parallel , to pump controller 8.
  • the load pressure p z1 and the equivalent pressure of the spring 18 counteract the pressure in the chamber 9, so that the compensating piston 10 adjusts itself automatically so that via the throttle point that forms 19 the flow rate is reduced to the load pressure p z1 .
  • the pressure drop at the throttle point 19 corresponds to the equivalent pressure of the spring 18 (this is relatively low, 1 to 8 bar).
  • the load pressure P z1 of the cylinder 1 is also fed to the further compensator pistons 14, 15 via the line 13. This pressure is also present in the spring spaces 22, 23 of the compensators 14 and 15 via the connecting channels 20, 21 running in the longitudinal direction.
  • the same pump pressure p p is reduced by the pressure drop through the control openings 5, 6, the pressure drops in the control openings 4, 5, 6 of all consumers 1, 2, 3 being the same in accordance with the LUDV principle.
  • the pressure in the pressure chambers 24, 25 is reduced by the throttle openings 26, 27 which are set according to the pressure compensator principle to the pressures p z2 or p z3 in the cylinders 2, 3 which are lower than the pressure p z1 in the cylinder 1.
  • the spherical closure elements 30, 31 are pressed onto their seats 28, 29 by the higher pressure p z1 introduced via the line 13 pressed so that oil flow from line 13 to cylinders 2 and 3 is prevented.
  • the spherical closure element 12 is lifted from its valve seat 32 as a result of the higher pressure prevailing in this compensator piston 10 and bears against a stop 33 of a closure element 34 inserted from above into the compensator piston 10, which at the same time guides the spring 18 in the spring chamber 17.
  • each compensator piston 10, 14, 15 is provided with channels 37, 38, 39 running in the longitudinal direction and in each case two channels 11, 41, 42, 43, 44, 45 running transversely thereto.
  • channels 16, 20, 21 are also incorporated in the longitudinal direction for connecting the cylinders 1, 2, 3 with the associated spring chamber 17, 22, 23.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)
EP96102897A 1995-03-24 1996-02-27 Dispositif pour une distribution du débit de fluide indépendante de la pression de charge des vannes de commande d'engins de chantier Expired - Lifetime EP0733743B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19510408 1995-03-24
DE19510408 1995-03-24
DE19520451 1995-06-03
DE19520451A DE19520451C1 (de) 1995-03-24 1995-06-03 Hydraulisches System

Publications (2)

Publication Number Publication Date
EP0733743A1 true EP0733743A1 (fr) 1996-09-25
EP0733743B1 EP0733743B1 (fr) 1999-06-30

Family

ID=26013593

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96102897A Expired - Lifetime EP0733743B1 (fr) 1995-03-24 1996-02-27 Dispositif pour une distribution du débit de fluide indépendante de la pression de charge des vannes de commande d'engins de chantier

Country Status (2)

Country Link
EP (1) EP0733743B1 (fr)
AT (1) ATE181755T1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3057309A1 (fr) * 2016-10-10 2018-04-13 Robert Bosch Gmbh Circuit hydraulique de commande multiple
CN109869362A (zh) * 2019-01-31 2019-06-11 中国铁建重工集团有限公司 用于模拟凿岩负载的液压系统和凿岩负载的模拟测试方法

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0411151A1 (fr) * 1989-02-20 1991-02-06 Hitachi Construction Machinery Co., Ltd. Circuit hydraulique pour machines
US5067389A (en) * 1990-08-30 1991-11-26 Caterpillar Inc. Load check and pressure compensating valve
EP0491050A1 (fr) * 1990-07-05 1992-06-24 Hitachi Construction Machinery Co., Ltd. Systeme de commande hydraulique et agencement de soupapes associees
WO1993021447A1 (fr) * 1992-04-10 1993-10-28 Kabushiki Kaisha Komatsu Seisakusho Soupape de commande a soupapes de compensation de pression

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0411151A1 (fr) * 1989-02-20 1991-02-06 Hitachi Construction Machinery Co., Ltd. Circuit hydraulique pour machines
EP0491050A1 (fr) * 1990-07-05 1992-06-24 Hitachi Construction Machinery Co., Ltd. Systeme de commande hydraulique et agencement de soupapes associees
US5067389A (en) * 1990-08-30 1991-11-26 Caterpillar Inc. Load check and pressure compensating valve
WO1993021447A1 (fr) * 1992-04-10 1993-10-28 Kabushiki Kaisha Komatsu Seisakusho Soupape de commande a soupapes de compensation de pression
GB2282678A (en) * 1992-04-10 1995-04-12 Komatsu Mfg Co Ltd Control valve with pressure compensator valves

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3057309A1 (fr) * 2016-10-10 2018-04-13 Robert Bosch Gmbh Circuit hydraulique de commande multiple
CN109869362A (zh) * 2019-01-31 2019-06-11 中国铁建重工集团有限公司 用于模拟凿岩负载的液压系统和凿岩负载的模拟测试方法

Also Published As

Publication number Publication date
EP0733743B1 (fr) 1999-06-30
ATE181755T1 (de) 1999-07-15

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