EP0877169A2 - Dispositif de commande hydraulique indépendante de la pression de charge d'un moteur à double effet - Google Patents

Dispositif de commande hydraulique indépendante de la pression de charge d'un moteur à double effet Download PDF

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Publication number
EP0877169A2
EP0877169A2 EP98102270A EP98102270A EP0877169A2 EP 0877169 A2 EP0877169 A2 EP 0877169A2 EP 98102270 A EP98102270 A EP 98102270A EP 98102270 A EP98102270 A EP 98102270A EP 0877169 A2 EP0877169 A2 EP 0877169A2
Authority
EP
European Patent Office
Prior art keywords
pressure
slide
control
control device
orifice
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
EP98102270A
Other languages
German (de)
English (en)
Other versions
EP0877169B1 (fr
EP0877169A3 (fr
Inventor
Wolfgang Koetter
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 EP0877169A2 publication Critical patent/EP0877169A2/fr
Publication of EP0877169A3 publication Critical patent/EP0877169A3/fr
Application granted granted Critical
Publication of EP0877169B1 publication Critical patent/EP0877169B1/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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15C—FLUID-CIRCUIT ELEMENTS PREDOMINANTLY USED FOR COMPUTING OR CONTROL PURPOSES
    • F15C3/00—Circuit elements having moving parts
    • F15C3/06—Circuit elements having moving parts using balls or pill-shaped disks
    • 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
    • F15B2211/30505—Non-return valves, i.e. 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
    • F15B2211/30—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
    • F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the directional control valve
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3127—Floating position connecting the working ports and the return line
    • 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
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle 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 is based on a hydraulic Control device for load pressure independent control of a double acting motor according to the in the preamble of Claim 1 specified genus.
  • Such a hydraulic control device is already used load pressure compensated control of a double acting Motors known from DE 36 34 728 C2, two of which Directional control valves for parallel actuation of the assigned Motors from a common variable displacement pump with pressure medium are supplied, the controller with a control line a shuttle valve chain with the maximum load pressure of the two motors is applied.
  • the pressure compensator used for load pressure compensation downstream of a metering orifice on the control slide, the Pressure compensator also used for direction control Piston sections of the control spool is connected upstream.
  • the Throttle valve in the downstream pressure compensator is in Opening direction from the pressure downstream of the orifice plate and in Closing direction of the highest load pressure and the Control pressure difference applied by the control spring.
  • DE 40 26 720 A1 is a hydraulic one Control device for load pressure independent control of a known double-acting engine, in which a pressure compensator upstream of that formed on the spool Orifice plate is switched.
  • This directional valve can be used with a check valve separated from the pressure compensator Meet security requirements, with discharge a cross channel between the check valve and orifice plate controlled via a piston section of the control slide which is also designed as a full slide valve. Also points the directional control valve has a second individual orifice Limit the oil flow to.
  • the hydraulic control device load-independent control of a double-acting Motors with the characterizing features of claim 1 on the other hand the advantage that it is at a supply-dependent oil flow distribution a higher degree Offers security and an extended usability. So can be separated by the arrangement of the pressure compensator of the check valve in connection with the control of the Pressure relief in the cross channel directly above the Control spool achieve that the load pressure with falling Pump pressure can be kept safer and faster. This also applies if the pressure in the control circuit Leakage or line break decreases.
  • the lines be formed as simply as possible in the control circuit, whereby Connecting lines in the spool itself are not required, see above that this as a simple, inexpensive building Full slide can be executed.
  • the directional control valve with a fourth Equip switching position for an open gear, the with the load pressure line connected to the pump is relieved.
  • a second individual orifice with this directional control valve integrate which the oil flow to the engine limited regardless of the deflection of the spool.
  • FIG. 1 shows a longitudinal section through a hydraulic control device with a directional valve and Combined pressure compensator in a simplified representation
  • figure 2 as a detail a shuttle valve from a control circuit according to II-II in Figure 1
  • Figure 3 is a schematic Representation of a control block for two double-acting Motors with two control devices according to FIG. 1.
  • Figure 1 shows a longitudinal section through a hydraulic Control device 10 for load pressure-independent control of a double-acting engine.
  • the control device 10 are the actual directional control valve 11 in the load-sensing version and the associated pressure compensator 12 in one common housing 13 arranged.
  • the housing 13 has one between the two end faces continuous longitudinal bore 14, in the ring-shaped Extensions trained a total of seven chambers 15 to 21 of which the five adjacent chambers 15 to 19 serve to control the direction of the pressure medium flow, while the two outer chambers 20, 21 one Measuring aperture 22 are assigned, which of Speed control of the engine is used.
  • the five adjacent chambers 15 to 19 serve the middle one Chamber as the inlet chamber 17, while those lying next to it two chambers a first motor chamber 16 and a second Form motor chamber 18, which with a motor connection 23 or 24 are connected.
  • 21 serves the first lying next to the second return chamber 19 Orifice chamber 20 as a discharge orifice chamber and the other as the inlet-side, second orifice chamber 21.
  • a spool 25 is tight and slidably guided.
  • the control slide 25 is by annular grooves divided into six piston sections 27 to 32.
  • the three adjacent piston sections 27, 28, 29 are with Control edges equipped and are used for directional control.
  • An adjoining fourth piston section 30, which in the drawn neutral position of the spool 25 in the outlet-side measuring orifice chamber 20 is used all to relieve a control circuit.
  • the one about it subsequent fifth piston section 31 is part of the Measuring aperture 22 and determines with its control edges Deflection of the control spool in both working positions the size of the volume flow to the motor and thus its speed.
  • the outer, sixth piston section 32 protrudes from the longitudinal bore 14 so that a Attack unspecified actuator can.
  • Control slide 25 with the first piston section 27 in one double-acting return device 33, the type of which is known per se and which the spool in its Neutral position 34 centered, out of which he in two Working positions 35 and 36 can be deflected. Furthermore, the Control slide 25 a fourth switching position 37, which as Free position is executed.
  • FIG. 1 also shows, is in the housing 13 below the longitudinal bore 14, a second bore 39 and below a third bore 41 is arranged, all parallel to the Longitudinal bore 14 run.
  • the second hole 39 is formed like a blind hole and takes up inside Check valve 42 with its spherical closing member 43 on.
  • the discharge-side orifice chamber 20 a perpendicular to Spool 25 extending extension 45, which intersects the third bore 41.
  • Extension 45 also extends in the housing 13 perpendicular to the longitudinal slide 25, a circulation chamber 46, in whose end near the slide opens into the second bore 39, while with its end facing away from the longitudinal slide 25 penetrates the third bore 41. That way forms one between the extension 45 and the circulation chamber 46 extending wall of the housing 13 an annular web 47, the both as a control edge for the second orifice 44, and serves for a throttle slide 48 of the pressure compensator 12.
  • Throttle slide 48 is a hollow slide with a Blind hole 49 and a radial bore 51 executed, see above that he is in the starting position centered by the control spring 52 the circulation chamber 46 with the discharge-side orifice chamber 20 connects in a throttled manner.
  • the throttle valve 48 occupies his working position in the company Connection controlled via the radial bore 51. Of the Throttle valve 48 is on its right front side Pressure in the extension 45 in the opening direction, that is acted against the force of the spring 52. In The closing direction acts on the throttle slide 48 the control spring 52 and the maximum load pressure in the spring chamber 53 via a control opening 54 from a control circuit is fed.
  • FIG. 1 also shows, lies in the second hole 39 in the area between the securing the inlet chamber 17 Check valve 42 and the circulation chamber 46 a Pressure tap opening 55, through which the maximum load pressure of the connected motor is tapped.
  • Form shuttle valve 56 and control channel 57 thereby parts of a control circuit 58 known per se, in which in a manner known per se via shuttle valve chains maximum load pressure selected and for a load sensing control is used.
  • FIG. 3 shows a schematic representation of a Control block in which, in addition to the first control device 10 a similar, second control device 70 are flanged together so that at least two double-acting motors can be operated in parallel.
  • the Control devices 10, 70 are between one Connection plate 71 and an end plate 73 switched and connected in parallel to the continuous inlet channel 61.
  • the inlet channel 61 is from a pressure medium supply unit 73 supplied with pressure medium, with the Control circuit 58 of the maximum load pressure is returned.
  • the shuttle valves 56 form in both Control devices 10, 70 a valve chain, via which the maximum load pressure is selected or one Relief of the control circuit 58 is made.
  • control device 10 The operation of the control device 10 is as follows explained, the basic function of such Load-sensing valves are assumed to be known per se.
  • the pressure compensator 12 Measuring aperture 20 is connected downstream and is also upstream from the directional control edges in the directional control valve 11.
  • the LS pressure tap that is, the one that taps the load pressure Pressure tap opening 55 in the directional control valve 11 lies between the Pressure compensator 12 and the check valve 42, so that the respective pressure signal via the shuttle valve 56 in the Control circuit 58 is given.
  • the one in the control circuit 58 selected, highest load pressure becomes pump 73 on the one hand and on the other hand into the spring chambers 53 of the pressure compensators 12 passed, this load pressure signal via control lines and the control openings 54 enter the spring chambers 53.
  • On the opposite end is the throttle slide 48 from the pressure downstream of the orifice 22 in the opening direction acted upon. This type of interconnection and the Pressurization of the throttle slide 48 enables one supply-dependent oil flow distribution at Parallel actuation of both control devices 10, 70.
  • control device 10 If the control device 10 is operated by itself and deflected into one of the working positions 35 or 36, so a load pressure independent control of the connected motor.
  • the throttle slide 48 in the pressure compensator 12 opens, controls he the relief connection via the radial bore 51 to.
  • the control edge also closes at the fourth piston section 30 the connection to the return chamber 19 before the orifice 22 opens. In this way there is no loss of oil to the return on.
  • the pressure compensator 12 maintains the pressure drop the measuring aperture 22 constant in a manner known per se, so that the speed of the motor proportional to the displacement of the spool 25 and regardless of Load pressure fluctuations is controlled. Should do this Leakage or a sticking shuttle valve the function of the Pressure compensator 12 may be impaired, in any case close the check valve 42 and prevent oil from the load flows towards the pump connection. Independent of the pressure conditions in the spring chamber 53 of the pressure compensator 12 a load on the motor becomes safe when the pump pressure drops held.
  • the check valve 42 designed as a seat valve ensures a low leakage.
  • downstream Pressure compensator 12 which keeps the pressure at the highest Load pressure plus regulating pressure difference regulates.
  • the Pressure differences at the orifice plates 22 become smaller and less oil flows to the engines.
  • the oil flow through the directional valves 11 increases in relation to the given Setpoints.
  • the directional valve 11 also has a fourth Switch position, this free position 37 by Pressing the control slide 25 into the housing 13 is achieved. Both are in this release position Motor connections 23, 24 with the return chambers 15 and 19 connected and the LS pressure line is relieved.
  • the volume flow can be independent of Limit the stroke of the control slide 25 for the directional valve 11, as is known in itself.
  • control spool 25 is designed as a full slide valve particularly advantageous combination.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Theoretical Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
EP98102270A 1997-05-07 1998-02-10 Dispositif de commande hydraulique indépendante de la pression de charge d'un moteur à double effet Expired - Lifetime EP0877169B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19719228A DE19719228A1 (de) 1997-05-07 1997-05-07 Hydraulische Steuereinrichtung zur lastdruckunabhängigen Steuerung eines doppeltwirkenden Motors
DE19719228 1997-05-07

Publications (3)

Publication Number Publication Date
EP0877169A2 true EP0877169A2 (fr) 1998-11-11
EP0877169A3 EP0877169A3 (fr) 2000-01-19
EP0877169B1 EP0877169B1 (fr) 2003-12-03

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP98102270A Expired - Lifetime EP0877169B1 (fr) 1997-05-07 1998-02-10 Dispositif de commande hydraulique indépendante de la pression de charge d'un moteur à double effet

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EP (1) EP0877169B1 (fr)
DE (2) DE19719228A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001092729A1 (fr) 2000-06-02 2001-12-06 Robert Bosch Gmbh Dispositif de commande hydraulique
WO2002012732A3 (fr) * 2000-08-08 2003-08-07 Husco Int Inc Systeme de vanne de regulation hydraulique a regulation de debit par compensation de pression

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109798270B (zh) * 2019-02-25 2020-05-19 哈尔滨工业大学 多模态节能伺服作动器及实现多模态节能的方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3629850A1 (de) * 1986-09-02 1988-03-03 Bosch Gmbh Robert Hydraulisches wegeventil
DE3634728A1 (de) * 1986-10-11 1988-04-21 Rexroth Mannesmann Gmbh Ventilanordnung zum lastunabhaengigen steuern mehrerer gleichzeitig betaetigter hydraulischer verbraucher
DE4026720A1 (de) * 1989-12-19 1991-06-20 Bosch Gmbh Robert Hydraulisches wegeventil
DE4136991A1 (de) * 1991-11-11 1993-05-13 Bosch Gmbh Robert Hydraulisches wegeventil
EP0550257A1 (fr) * 1991-12-25 1993-07-07 Kayaba Industry Co., Ltd. Dispositif de commande pour plusieurs servomoteurs

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3629850A1 (de) * 1986-09-02 1988-03-03 Bosch Gmbh Robert Hydraulisches wegeventil
DE3634728A1 (de) * 1986-10-11 1988-04-21 Rexroth Mannesmann Gmbh Ventilanordnung zum lastunabhaengigen steuern mehrerer gleichzeitig betaetigter hydraulischer verbraucher
DE4026720A1 (de) * 1989-12-19 1991-06-20 Bosch Gmbh Robert Hydraulisches wegeventil
DE4136991A1 (de) * 1991-11-11 1993-05-13 Bosch Gmbh Robert Hydraulisches wegeventil
EP0550257A1 (fr) * 1991-12-25 1993-07-07 Kayaba Industry Co., Ltd. Dispositif de commande pour plusieurs servomoteurs

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001092729A1 (fr) 2000-06-02 2001-12-06 Robert Bosch Gmbh Dispositif de commande hydraulique
US6874526B2 (en) 2000-06-02 2005-04-05 Robert Bosch Gmbh Hydraulic control device
WO2002012732A3 (fr) * 2000-08-08 2003-08-07 Husco Int Inc Systeme de vanne de regulation hydraulique a regulation de debit par compensation de pression

Also Published As

Publication number Publication date
DE59810308D1 (de) 2004-01-15
EP0877169B1 (fr) 2003-12-03
DE19719228A1 (de) 1998-11-12
EP0877169A3 (fr) 2000-01-19

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