EP2469103A2 - Entraînement hydraulique - Google Patents

Entraînement hydraulique Download PDF

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Publication number
EP2469103A2
EP2469103A2 EP20110008970 EP11008970A EP2469103A2 EP 2469103 A2 EP2469103 A2 EP 2469103A2 EP 20110008970 EP20110008970 EP 20110008970 EP 11008970 A EP11008970 A EP 11008970A EP 2469103 A2 EP2469103 A2 EP 2469103A2
Authority
EP
European Patent Office
Prior art keywords
pressure
control
drive according
oil supply
line
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.)
Withdrawn
Application number
EP20110008970
Other languages
German (de)
English (en)
Other versions
EP2469103A3 (fr
Inventor
Michael Schütte
Peter LÖWE
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 EP2469103A2 publication Critical patent/EP2469103A2/fr
Publication of EP2469103A3 publication Critical patent/EP2469103A3/fr
Withdrawn legal-status Critical Current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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/28—Other constructional details
    • B66D1/40—Control devices
    • B66D1/42—Control devices non-automatic
    • B66D1/44—Control devices non-automatic pneumatic of hydraulic
    • 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
    • F15B2211/31—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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • 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
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members
    • 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
    • F15B2211/76—Control of force or torque of the output member
    • F15B2211/761—Control of a negative load, i.e. of a load generating hydraulic energy

Definitions

  • the invention relates to a hydraulic drive according to the preamble of claim 1.
  • a generic hydraulic drive for a winch is known in which a winch drum is driven by a hydraulic motor.
  • the inlet of the hydraulic motor is connected to a pump, preferably a variable displacement pump.
  • the hydraulic fluid flowing from the hydraulic motor flows through the return to a tank T out.
  • a pulling load acts on the winch drum, it can accelerate at insufficient deceleration so that the pumped by the pump pressure medium flow is not sufficient to supply the hydraulic motor with enough pressure medium, so that corresponding to the pressure drops in the inlet and in unfavorable conditions even cavitation phenomena may occur.
  • a brake valve also called lowering brake valve provided, which is biased in a closed position and is acted upon in the opening direction by the pressure in the respective inlet.
  • this brake valve is designed so that it is effective in both directions of rotation of the hydraulic motor, ie with alternating supply and return.
  • the brake valve is brought into an open position, so that the effluent from the hydraulic motor pressure medium flow rate flows through the brake valve to the tank.
  • the pressure medium volume flow flowing toward the tank is throttled or blocked, so that the hydraulic motor is decelerated accordingly and the pressure in the inlet rises until the brake valve opens again.
  • such hydraulic drives are used for example in winches, in which the drive is usually acted upon only in one direction by the load to be moved via the winch.
  • the drive When lowering such a pulling load, it may come to the initially mentioned Kavitationsproblemen in the inlet, which are minimized by suitable control of the brake valve.
  • For stable control of such a brake valve is usually provided in the inlet at least a pressure of 20 bar.
  • the winch drum is assigned a mechanical holding brake, which can be hydraulically ventilated. This airing is done by the inlet pressure, with a pressure of at least 20 bar is required for this ventilation.
  • the invention has for its object to provide a hydraulic drive in which the energy losses are reduced when braking a towing load.
  • the hydraulic drive has a hydraulic motor whose inlet is connected to a pressure medium source, for example a pump and in whose return a brake valve is arranged, that is acted upon by a tapped via a control line control pressure in the direction of an open position.
  • the hydraulic drive has a control valve device controlled by the inlet pressure, which generates the control pressure. That the control pressure for opening the brake valve is thus not tapped at the inlet, so that corresponding to the throttle to be degraded in the return to the opening effective direction on the brake valve control pressure is reduced - the hydraulic losses when braking a towing load are thus significantly reduced.
  • the control valve device is designed in such a way that it generates the effective control of the actuation of the brake valve control pressure in a suitable manner.
  • control valve device is designed with an adjustable and a fixed throttle.
  • the control pressure for actuating the brake valve is tapped between the two throttles, which thus form a pressure divider for tapping the appropriate control pressure.
  • the hydraulic drive can be designed with its own control oil supply, to which an input port of the control valve device is connected and whose output port is in fluid communication with a control oil supply line from which the control line branches off.
  • the control oil supply line may be connected to a leakage or flushing connection.
  • control pressure relief valve To increase the reliability of the maximum control pressure is limited by a control pressure relief valve.
  • the control oil supply is preferably carried out with a control oil pump whose pump pressure is limited to a maximum value.
  • the adjustable throttle of the control valve device may be a continuously adjustable 3/2-way valve, so that the control pressure is adjusted by means of a 2-edge control.
  • the control valve device is preferably designed such that, in a basic position, it depressurizes the control oil supply line, for example towards a tank.
  • the directional valve is acted upon by the inlet pressure in the direction of an open position in which a connection between the control oil supply and the control oil supply line is opened and controlled in accordance with their connection to the tank.
  • damping nozzles can be provided in the control oil supply line. These are for example designed as throttle check valves.
  • a nozzle is provided in the return from the hydraulic motor to a tank through which changes in the return flow rate are converted into a change in the return pressure.
  • the hydraulic drive can be designed as a closed or open circuit.
  • the hydraulic motor drives a winch drum, which can be fixed via a mechanical brake.
  • a brake can be ventilated for example by the inlet pressure.
  • the in FIG. 1 shown hydraulic drive 1 has a variable displacement pump 2, via which a hydraulic motor 4 is driven with adjustable displacement. This in turn can drive, for example, a winch or the like.
  • the variable displacement pump 2 is designed for example as an axial piston pump, wherein a pivot angle is variable to adjust the delivery volume.
  • the swivel angle can be detected via a swivel angle sensor 6.
  • the variable displacement pump 2 is designed with a conventional pump control, which allows, for example, the Pump pressure to maintain a predetermined pressure difference above the individual load pressure in the system. Such pressure and flow control systems are known, so that further explanations are unnecessary.
  • the drive 1 according to FIG. 1 is designed as an open circuit. Accordingly, the pressure medium is conveyed by the variable displacement pump 2 via an inlet 8 to an inlet port of the hydraulic motor 4 and flows from this via a return line 10 to a tank T out from where the variable displacement 2 sucks pressure medium. With relatively long supply lines, these can represent a considerable capacity volume for the pressure medium; this capacity volume is shown in the illustration FIG. 1 provided with the reference numeral 12.
  • the pressure fluid flow direction to and from the hydraulic motor 4 is adjusted via a directional control valve 6, which thus determines the direction of rotation of the hydraulic motor 4.
  • the directional control valve 6 is designed as a continuously adjustable directional control valve, as it is commonly used to control pressure medium flows.
  • the directional control valve 6 is spring-biased in a basic position in which a residual opening is present, in which the inlet 8 and the return 10 are connected via throttles and a connected to a tank port T tank line 13 to the tank T.
  • a pressure port P of the directional control valve 6 is connected via a pump line 12 to the pressure connection of the variable displacement pump 2.
  • the two working ports A, B of the directional control valve 6 are connected to the inlet 8 and the return 10.
  • the adjustment of the directional control valve is electrically or electro-hydraulically (not shown), wherein in an adjustment in the direction a of the working port A to the tank port T and the pressure port P is connected to the working port B (lifting), while at an adjustment in direction b (lowering ) the pressure medium is fed into the inlet 8 and flows from the hydraulic motor 4 via the return line 10, the working port B and the tank port T and arranged in the tank line 13 nozzle 40 to the tank T out. Due to the pressure drop across this nozzle 40 pressure medium volume flow fluctuations are converted into corresponding pressure changes acting on the brake valve 16 via the brake control line 20 in the closing direction.
  • the variable displacement pump 2 is designed with a brake valve device 14, which in FIG. 1 indicated by dashed lines.
  • This brake valve assembly 14 has a brake valve 16 which is biased by a spring 18 and a first brake valve control line 20 in a closed position. In an opening direction, the pressure acts in a control line 22, via which an effective control pressure in the opening direction is controlled.
  • the brake valve 16 is designed as a continuously adjustable directional control valve with three ports P, Q, C, wherein in the spring-biased locking position connected to a port P feed line 24 is shut off upstream of a check valve 26 from the inlet 8. Another connection Q is connected via a feed line 28 to the inlet 8. Not shown in FIG.
  • FIG. 1 are positions of the brake valve 16 in which it opens up a pressure medium connection from port Q to port C. In this case, the pressure would then act in the opening direction in the now designated drain line 10 - this configuration would then be effective in a reversal of the direction of rotation of the hydraulic motor 4.
  • a winch drum is usually in FIG. 1 shown sufficient configuration, since the load L always acts in one direction and accordingly the Kavitations- and vibration problem occurs only in one direction of rotation of the hydraulic motor 4 when lowering
  • An output terminal C of the brake valve 16 is connected to a branching output line 30, which are connected via two branch lines 30a, 30b and each arranged therein, designed as check valves feed valves 32, 34 with the return 10 and the inlet 8 are connectable. These feed valves 32, 34 open towards the return 10 and to the inlet 8.
  • the greater of the pressures in the inlet 8 and in the return 10 is tapped via a shuttle valve 36 and guided to a control port G of the brake valve assembly 14.
  • the area between the two feed valves 32, 34 is connected via a purge line 38 with a purge port S.
  • the control valve 22 acting on the brake valve 16 with a control pressure acting in the opening direction is connected in a cover 42 to a control oil supply line 44, which are connected via two connections M of the cover 42 with control oil line sections, which are also referred to as control oil supply line 44 for the sake of simplicity goes through the lid.
  • a control pressure limiting valve 46 is provided, which is designed to be electrically adjustable, so that the maximum pressure in the control oil supply line 44 can be changed.
  • the boundary area can be, for example, in the range of 0 to 80 bar.
  • a damping throttle assembly 48 is provided which is formed by two parallel, oppositely effective throttle check valves.
  • a throttle 52 is provided with a fixed cross-section.
  • the part of the control oil supply line 44 arranged in the figure to the left of the connection Mp of the cover 42 is connected to an output connection A of a continuously adjustable control valve 54.
  • This is designed as a continuously adjustable 3/2-way valve and biased by a spring in a basic position in which the output port A is connected to a tank port S, which in turn is in fluid communication with the tank T.
  • a pressure port P of the control valve 54 is shut off.
  • This pressure port P is connected via a control pump line 56 to a control oil pump 57, which is designed for example as a fixed displacement pump.
  • the maximum pressure in the control pump line 56 is over Pump pressure limiting valve 58 limited to a maximum pressure of for example 100 bar.
  • the directional control valve 54 is in the opening direction, i. in a direction in which the pressure port P is connected to the output port A, acted upon via a control line 60 with the pressure in the inlet 8.
  • the spring 62 acting on the control valve 54 in the closing direction corresponds to a pressure equivalent of approximately 10 to 20 bar, so that the control valve 54 is displaced in the direction of its control position when a corresponding pressure in the inlet 8 is exceeded.
  • the applied in the control pump line 56 control pressure is thus throttled via the continuously adjustable control valve 54 and forms together with the fixed throttle 52 a pressure divider which determines the pressure in the control line 22 in dependence on the inlet pressure and the setting of the spring 62.
  • the two series-connected throttles control valve 54 and throttle 52
  • thus together form a control valve device for generating a control pressure.
  • control valve device is controlled as a function of the pressure in the inlet 8.
  • an output shaft 64 of the hydraulic motor 4 is connected via a coupling 66 to a winch drum 68 for raising or lowering a load L.
  • the winch drum 68 is associated with a mechanical holding brake 70, which is biased by a spring in the direction of braking engagement and can be hydraulically ventilated via a ventilation line 72 to cancel the braking intervention. This venting is done by the pressure in the inlet 8, wherein the braking intervention should be canceled before the brake valve 16 is adjusted in the direction of its open position. That is, the pressure required for releasing the holding brake 70 is slightly below the response pressure of the brake valve 16 also in the range of 10 to 20 bar.
  • a significant advantage of the above-described solution is that on the described control valve device with the adjustable throttle (control valve 54) and the fixed throttle (throttle 52), a control pressure for the brake valve 16 is generated, although it depends on the pressure in the inlet 8, but not must be generated via the variable displacement pump 2, so that via the throttle 40 to be destroyed "pressure difference and thus the hydraulic loss to that part is less, which is generated via the described control valve device in the control line 22 and acts in the opening direction on the brake valve 16 ,
  • a hydraulic drive with a hydraulic motor, which is associated with a brake valve, which is acted upon by a control pressure in the opening direction, which is generated via a control of the inlet pressure control valve device.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Braking Systems And Boosters (AREA)
  • Regulating Braking Force (AREA)
EP20110008970 2010-12-22 2011-11-11 Entraînement hydraulique Withdrawn EP2469103A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201010055718 DE102010055718A1 (de) 2010-12-22 2010-12-22 Hydraulischer Antrieb

Publications (2)

Publication Number Publication Date
EP2469103A2 true EP2469103A2 (fr) 2012-06-27
EP2469103A3 EP2469103A3 (fr) 2014-10-08

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ID=45218161

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20110008970 Withdrawn EP2469103A3 (fr) 2010-12-22 2011-11-11 Entraînement hydraulique

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EP (1) EP2469103A3 (fr)
DE (1) DE102010055718A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014001043A1 (fr) * 2012-06-29 2014-01-03 Robert Bosch Gmbh Dispositif d'entrainement hydraulique
GB2533034A (en) * 2014-11-03 2016-06-08 Husco Int Inc Systems and methods for flow summation in a hydraulic system with open center control valves
CN111891946A (zh) * 2020-07-29 2020-11-06 徐州重型机械有限公司 一种动力输送系统、方法及起重机

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012006551B4 (de) 2012-04-02 2022-10-20 Wessel-Hydraulik Gmbh Hydraulische Schaltungsanordnung
DE102012020821B4 (de) 2012-10-23 2021-07-15 Liebherr-Werk Ehingen Gmbh Notantrieb für ein Baugerät und Verfahren zum Betrieb des Notantriebs
DE102016201971B4 (de) * 2016-02-10 2021-04-22 Robert Bosch Gmbh Hydraulische Antriebsvorrichtung mit lastabhängigem Druckteiler
CN113357209B (zh) * 2021-04-22 2023-09-19 武汉船用机械有限责任公司 石油钻机的升降液压系统
DE102022205361A1 (de) 2021-06-29 2022-12-29 Robert Bosch Gesellschaft mit beschränkter Haftung Seilwinde mit druckabhängiger Verstellung des wenigstens einen Hydromotors

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10320946B4 (de) 2003-05-09 2005-05-04 Bauer Maschinen Gmbh Seilwindenanordnung und Verfahren zu deren Betrieb
DE102008064064A1 (de) 2008-12-19 2010-06-24 Robert Bosch Gmbh Hydraulische Steueranordnung

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2553598Y2 (ja) * 1992-02-24 1997-11-05 株式会社タダノ 油圧駆動ウインチの寸落防止装置
JP3294183B2 (ja) * 1998-01-13 2002-06-24 住友重機械建機クレーン株式会社 油圧ウインチのカウンタバランス回路
JP2000220606A (ja) * 1999-01-29 2000-08-08 Kobe Steel Ltd 液圧ウィンチ回路

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10320946B4 (de) 2003-05-09 2005-05-04 Bauer Maschinen Gmbh Seilwindenanordnung und Verfahren zu deren Betrieb
DE102008064064A1 (de) 2008-12-19 2010-06-24 Robert Bosch Gmbh Hydraulische Steueranordnung

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014001043A1 (fr) * 2012-06-29 2014-01-03 Robert Bosch Gmbh Dispositif d'entrainement hydraulique
CN104379972A (zh) * 2012-06-29 2015-02-25 罗伯特·博世有限公司 液压驱动装置
CN104379972B (zh) * 2012-06-29 2016-09-28 罗伯特·博世有限公司 液压驱动装置
GB2533034A (en) * 2014-11-03 2016-06-08 Husco Int Inc Systems and methods for flow summation in a hydraulic system with open center control valves
GB2533034B (en) * 2014-11-03 2020-09-09 Husco Int Inc Systems and methods for flow summation in a hydraulic system with open center control valves
CN111891946A (zh) * 2020-07-29 2020-11-06 徐州重型机械有限公司 一种动力输送系统、方法及起重机

Also Published As

Publication number Publication date
EP2469103A3 (fr) 2014-10-08
DE102010055718A1 (de) 2012-06-28

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