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EP1766146B2 - Systeme de soupapes de mecanisme de levage - Google Patents

Systeme de soupapes de mecanisme de levage Download PDF

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Publication number
EP1766146B2
EP1766146B2 EP05772453.6A EP05772453A EP1766146B2 EP 1766146 B2 EP1766146 B2 EP 1766146B2 EP 05772453 A EP05772453 A EP 05772453A EP 1766146 B2 EP1766146 B2 EP 1766146B2
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
lifting gear
valve arrangement
working
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.)
Expired - Lifetime
Application number
EP05772453.6A
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German (de)
English (en)
Other versions
EP1766146B1 (fr
EP1766146A1 (fr
Inventor
Sönke Jessen
Gerhard Keuper
Heinrich Lödige
Reiner Kunz
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
Bosch 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
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Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1766146A1 publication Critical patent/EP1766146A1/fr
Application granted granted Critical
Publication of EP1766146B1 publication Critical patent/EP1766146B1/fr
Publication of EP1766146B2 publication Critical patent/EP1766146B2/fr
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    • 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
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • 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
    • E02F9/2228—Control of flow rate; Load sensing arrangements using pressure-compensating valves including an electronic controller
    • 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
    • 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
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • 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
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F15B11/15—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor with special provision for automatic return
    • 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
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and 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
    • F15B2211/305—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
    • F15B2211/30545—In combination with a pressure compensating valve the pressure compensating valve is arranged between output member and 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5153—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a 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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/526—Pressure control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief 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
    • F15B2211/50—Pressure control
    • F15B2211/57—Control of a differential pressure
    • 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
    • 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
    • F15B2211/63—Electronic controllers
    • 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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6653—Pressure 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
    • F15B2211/70—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
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members

Definitions

  • the invention relates to a hoist valve arrangement for controlling a double-acting hoist or an attachment of a mobile working device according to the preamble of claim 1.
  • a hoist valve arrangement for controlling a double-acting hoist or an attachment of a mobile working device according to the preamble of claim 1.
  • Such an arrangement is known from the DE 41 35 013 A1 known.
  • FIG. 1 shows the basic structure of the working hydraulics of a tractor 1 or another mobile working device.
  • the tractor 1 is in accordance with Figure 1 with a rear linkage 2 and a front linkage 4, the lifting cylinders 6, 8 of which can be supplied with pressure medium from a hydraulic pump 12 via a control block 10.
  • the two hoists 2, 4 are single-acting (ew) - however, solutions are also known in which both the front lifting mechanism 4 and the rear lifting mechanism 2 are double-acting (dw).
  • the control block 10 contains electrohydraulically actuated directional valves 14 assigned to each of the consumers 6, 8, etc., which are controlled by an electrical control device 16.
  • the setpoints are set, for example, via a front control panel 18 or a rear control panel 20, which are arranged in the interior of the tractor cab 22, or via a rear button 22 on the rear of the tractor or a front button (not shown).
  • a plurality of sensors for example pressure sensors 26, speed sensors 28, position sensors 30, force sensors 32 or speed sensors 34, are provided on the tractor 1 to detect the forces, pressures, speeds and hoist positions, the signals of which can be processed via the control unit 16.
  • the rear linkage 2 is designed to be single-acting, the lifting cylinder 6 being extended by supplying pressure medium via the pump 12 and the lowering being carried out by the dead weight of the rear linkage 2 and any device attached to it, such as a plow 36 .
  • the rear linkage 2 is brought into a floating position so that the attachment rests on the ground due to its own weight and runs over any unevenness in the ground.
  • the contact pressure cannot be actively changed with the conventional single-acting rear linkages, since these linkages cannot be operated in the "press" work area.
  • the double-acting rear linkages 2 make it possible to actuate the lifting cylinder 6 in the “pushing” direction, so that, for example, active plowing is enabled.
  • This operating state can also be used, for example, to lift the rear of the tractor when changing the rear, large wheels so that it stands on the swinging front axle and on the attachment operated by the rear linkage or directly on the lower links.
  • the pressure sensor used up to now, for example in the front linkage, is arranged on the stretcher side, there is relief pressure regulation - the contact pressure remains unknown or is not used for regulation.
  • the invention has for its object to provide a hoist valve arrangement which makes it possible to set and limit a contact pressure with minimal effort.
  • the hoist valve arrangement has a continuously adjustable directional valve, to which one or more pressure compensators are connected upstream or downstream. Two working connections of the hoist valve arrangement are connected to the pressure chambers of the hoist, or more precisely the lifting cylinder of the hoist, which are effective in the lifting or lowering direction.
  • a proportionally adjustable pressure relief valve is provided in a working line, by means of which the pressure in this working line can be limited to a variable maximum value.
  • the pressure in this working line is limited via the pressure limiting valve as a function of certain operating states, so that the contact pressure can be variably adjusted accordingly.
  • hoist is generally to be understood as a device by means of which a work tool, attachment or the like assigned to a mobile working device can be moved or pressed against a reference plane.
  • This very simply constructed hoist valve arrangement makes it possible to adapt the contact pressure to different operating conditions in an extremely simple and cost-effective manner by actuating the pressure limiting valve.
  • the maximum pressure can be set via the pressure relief valve in a range between 0 to Adjust 250 bar.
  • a minimum contact pressure for example 5 to 8 bar
  • the function of the lifting mechanism designed with the lifting mechanism valve arrangement according to the invention is the same as that of a single-acting lifting mechanism.
  • the driver sets the pressure relief valve to its maximum value so that the contact pressure can correspondingly reach a maximum value.
  • the maximum pressure is set as a function of different operating states - for example when lifting the rear axle for changing the tires, when actuating a rapid feed switch for the quickest lowering movement, when actuating the rear button, etc., suitable maximum pressures being set in each case.
  • the driver sets the maximum pressure.
  • the control takes place according to the invention via a control unit, via which the continuously adjustable directional valve can be adjusted into a neutral position (dw) or into a floating position (ew) after the pressure limiting valve has responded.
  • a secondary pressure relief valve is preferably provided in the working line connected to the pressure chamber acting in the "lifting" direction.
  • a sink module is provided downstream of the two output connections of the continuously adjustable directional valve, which acts in a basic position as an unlockable check valve and acts as a discharge pressure compensator when a control pressure is applied.
  • the hoist valve arrangement according to the invention is preferably designed as an LS system, the pressure compensator being designed as an individual pressure compensator, which is followed by a continuously adjustable directional control valve which forms a variable measuring orifice.
  • the pressure compensator is acted upon by the highest load pressure of the controlled consumers in the opening direction. This highest load pressure is also reported to a pump and this is regulated in such a way that a pump pressure that is above the load pressure by a predetermined pressure difference is present in the pump line.
  • the hoist valve arrangement can be designed with a manually operated emergency drain, via which the working line carrying the higher pressure can be connected to the tank.
  • the solution according to the invention is preferably used in a rear linkage of a tractor.
  • attachments for example plowing and outside agricultural applications, for example for actuating shields, as are used, for example, in snow clearers.
  • a rear linkage 2 according to Figure 1 can - as in Figure 2 shown - use in different operating states.
  • the rear linkage and, accordingly, any attachments 36 operated therefrom are either lifted off the ground or are carried in contact with the ground with a predetermined supporting force.
  • This work area occurs, for example, when plowing or cultivating.
  • FIG 2 the lifting force curve is shown on the left above the lifting height - this lifting force must be applied by the lifting cylinder 6 of the rear lifting mechanism 2.
  • a load-free intermediate position is assumed in which the rear linkage 2 is not subjected to a force, so that the attachment rests on the ground due to its own weight.
  • Such a load-free intermediate position is usually set - as described below - by moving the directional valve 44 into a floating position.
  • the rear linkage 2 can be controlled in such a way that one in the direction of the ground in order to set the working area “pressing” acting pressure force is applied. Such an adjustment is required, for example, when plowing is active or with a packer. In the "press" work area, the rear axle of the tractor 1 can also be raised, so that a tire change is possible.
  • the compressive force effective in the “pressing” working area can be limited to different values, this limit value being varied as a function of the operating states described in more detail below.
  • FIG 3 a circuit diagram of a rear linkage 2 is shown, which is controlled via a linkage valve arrangement 14 according to the invention.
  • This is accommodated in a disk-shaped housing and has a pressure port P, a tank port T and two working ports A, B.
  • the pressure port P is connected via a pump line to a variable displacement pump 38, the delivery pressure of which depends on the highest, at the consumers of the Tractor 1 applied load pressure is set.
  • This load pressure is tapped at an LS connection.
  • a LS control is not a prerequisite for the system according to the invention.
  • the pressure port P is connected via an inlet channel 40 to an inlet port P 'of an individual pressure compensator 42, the outlet port A' of which is connected to an inlet port P "of a continuously adjustable directional valve 44.
  • Its return port R is connected via a return channel 46 to the tank port T of the hoist valve arrangement 14
  • the directional control valve 44 has two working connections A “and B" which are connected via working channels 48, 50 to the two working connections A, B of the hoist valve arrangement 14.
  • a lowering module 52, 54 is provided in each working channel 48, 50, which in a basic position serves as an unlockable check valve for clamping the lifting cylinder 6 of the rear linkage 2 without leaking oil and in a control position controls the pressure medium volume flow flowing back from the lifting cylinder 6 in the sense of a sequence control.
  • the working channel 50 can be connected downstream of the sink module 54 to the tank connection T via a pilot-controlled proportionally adjustable pressure relief valve 56.
  • the pressure in the other working channel 48 is limited by a secondary pressure relief valve 58.
  • the lifting cylinder 6 is double-acting, an annular space 60 effective in the “lowering” direction being connected to the working connection B and the pressure chamber 62 acting in the “lifting” direction being connected to the working connection A of the lifting gear valve arrangement 14.
  • An arm 66 pivotably mounted on a lifting shaft 64 and further coupling elements are actuated via the lifting cylinder 6, to which, for example, an attachment, such as a seed drill or a plow 68, is attached.
  • a pressure compensator piston 69 of the pressure compensator 42 is acted upon by a pressure compensator spring 70 and by the pressure in the opening direction tapped via a duct 72 by a load-reporting duct 74 connected to the LS connection and by the pressure in a control duct 76 in the closing direction, which is between the pressure compensator 42 and the directional valve 44 branches off from the inlet channel 40.
  • the LS channel 74 leads to a control connection LS "of the directional control valve 44. This has two further control connections X, to which control connections XA and XB are assigned on the output side.
  • the directional valve 44 is actuated via an in Figure 5 shown pilot valve 78 or a pilot valve arrangement, which in the illustration according to Figure 4 is formed by two electro-hydraulic pilot control elements 75, 77.
  • the triangle 79 indicates the pressure supply of these pilot control elements 77, 75.
  • Control oil can be supplied to a control chamber of the directional control valve 44 via the pilot valve 78 or the pilot control elements 77, 75, until a valve slide 80 assumes a working position. This is recorded via a displacement sensor 128. As soon as the desired position is reported by the displacement sensor 128, the pilot control element 77, 75 is brought back into its neutral position.
  • the position of the valve spool 80 is maintained in a controlled manner by actuating the pilot elements 77, 75 in accordance with the signal from the displacement sensor 128.
  • the pilot control elements 77, 75 are connected to the pressure supply 79 via control lines 82 and 84, respectively.
  • the valve slide 80 is biased by a centering spring arrangement 86 into its basic position (0) shown, in which the LS channel 74 is connected to the tank channel 46 and all other aforementioned connections are blocked.
  • valve bodies of the two sink modules 52, 54 are each acted upon by a spring 88 and by the individual load pressure tapped at the outlet A "or B" via pressure compensator channels 90, 92 downstream of the directional control valve 44 into their basic position (a), in which the modules 52, 54 act as check valves which allow a pressure medium flow to the connections A, B.
  • the valve bodies of the sink modules 52, 54 are each acted upon by the control pressure present at the connection XA or XB, which is tapped via an unlocking channel 94, 96.
  • This control pressure can correspond, for example, to the inlet pressure of the pilot valve arrangement 78.
  • the structure of the hoist valve arrangement with the individual pressure compensator 42, the continuously adjustable directional valve 44 and the two downstream sink modules 52, 54 essentially corresponds to the conventional solution of the valve SB23 LS, so that only the elements essential for understanding the invention are described below and in remaining in this regard reference is made to the existing state of the art for the directional control valve SB23 LS.
  • the valve slide 80 of the directional control valve 44 is displaced into one of its control positions marked with (b) via the pilot valve arrangement 78.
  • a measuring orifice is activated, which is connected downstream of the individual pressure compensator 42.
  • the pressure compensator 42 sets itself in a control position in which the pressure drop across the orifice plate is kept constant and thus a pressure medium volume flow independent of the load pressure is set.
  • This pressure medium volume flow is in the control positions marked with (b) via the pressure compensator 42, the pressure port P "and the output port A" of the directional control valve 44 to the input port PDW of the sink module 52 and via its output port ADW to the working port A of the hoist valve arrangement 14 and from there into the pressure chamber 62 on the bottom - the lifting cylinder 6 extends.
  • the pressure medium displaced from the annular space 60 flows via the working connection B of the hoist valve arrangement 14, the working channel 50, the output connection BDW and the input connection PDW of the sink module 54 to the connection B "of the directional control valve 44 and from there via the return connection R, the tank channel 46 and the This return flow is made possible by tapping the inlet pressure applied to the pilot valve arrangement 78 via the control port X and the outlet port XB of the directional control valve 44 and acting on the valve body in the opening direction via the unlocking channel 96, so that the sink module 54 unlocks and the Back flow of the pressure medium to the tank T is made possible. In these positions of the sink module 54 marked with (b), this acts as a discharge pressure balance via which the pressure medium volume flow running off is regulated to a certain extent.
  • the directional control valve 44 is shifted into one of its control positions marked with (a), so that the pressure medium supply via the lowering module 54 takes place in its non-return function to the annular space 60, while the pressure medium flowing out from the bottom-side pressure space 62 occurs via the unlocked sink module 52 and the directional control valve 44 flows out to the tank. Unlocking takes place via the control pressure, which is guided via the control connections X, XA of the directional control valve 44 and the unlocking channel 94 to the control surface of the sink module 52 which is effective in the opening direction.
  • the directional control valve 44 is moved into its floating position (end position c), in which both sink modules 52, 54 are unlocked and moved into their passage position marked with (b) and the working connections A, B and the control connection LS are connected to the tank connection T. and the input port P "is shut off.
  • the maximum pressure in the working channel 50 is limited to a value of, for example, between 0 and 250 bar by suitable setting of the proportionally adjustable directional valve 44.
  • FIG. 5 shows a section through a valve disc through which the lifting gear valve arrangement 14 is realized.
  • the valve disc has a disc-shaped housing 98, in which the pressure compensator 42, the directional control valve 44, the two sink modules 52, 54, the pilot valve 78, the secondary pressure relief valve 58 and the proportionally adjustable pressure relief valve 56 are integrated.
  • valve disc 98 shown furthermore contains an only schematically illustrated and manually operable emergency drain valve 100, via which the working channels 48 and 50 can be connected to the tank T.
  • the emergency drain valve 100 is arranged in a connecting channel 102 between the working channels 48, 50. It has a ball 104 which is biased by a grub screw 106 accessible from the outside into a closed position in which a connection to the tank channel 46 and thus to the return port R is blocked. By loosening the grub screw 106, the previously clamped ball 104 is released and can therefore be brought into an open position by the higher pressure in the working channel 48 or 50, in which the connection to the tank channel 46 is open - the pressure medium can come from the pressurized working channel 48 or 50 be drained.
  • connection A Via the secondary pressure relief valve 58, the pressure in the working channel 48 (connection A) is limited to a maximum pressure set below the pump pressure.
  • the construction of such secondary pressure relief valves is known, so that further explanations are unnecessary.
  • the design of the pilot-controlled, proportionally adjustable pressure relief valve 56 is also known per se - a piston 108 of the pressure relief valve 56 is loaded into a closed position against a valve seat by a weak compression spring 110 and by the pressure in the spring chamber. The pressure in the spring chamber is limited by the force applied to a closing cone 114 by means of a proportional magnet 112.
  • the proportional magnet 112 is controlled in the manner described below via the control device 16.
  • the lifting and lowering modules 52, 54 likewise have a conventional structure, with a module piston 116 being biased into a closed position via a closing spring 118.
  • the spring chamber of the closing spring 118 is acted upon by the pressure in the working channel 48 or 50 in the closed position of the module piston 116.
  • a pilot valve body 120 is arranged in the bottom of the module piston 116, which is also biased into its closed position via the closing spring 118 and thereby closes a pilot opening.
  • the pilot valve body 120 has a projection which can be brought into abutment with an opening piston 122.
  • the pressure on the control port XA (XB) can be applied to the back of this push-up piston, which pressure can be tapped off via the directional control valve 54 and its port X.
  • Reference numerals 124, 126, 130, 132, 134 denote pressure sensors, via which the pressures in the working channels 48, 50, the pressure at the pressure port P, the load pressure and other pressures can be detected.
  • the pilot valve 78 is designed as a 4/3-way valve, the output connections of which are connected to the control lines 82 and 84, which lead to the front-side control spaces 136 and 138 of the directional valve 44.
  • a one-way sensor 128 is arranged, via which the valve spool stroke can be detected.
  • the pilot valve 78 is activated in such a way that a control pressure difference acts in the control rooms 136, 138, through which the valve spool 80 moves out of the position shown in FIG Figure 5 shown spring-biased basic position is shifted to the left, so that pressure medium from the pressure port P, via the pressure compensator 42, the branching input port P "of the directional control valve 44, its output port B", the sink module 54 opening in its check valve function and the working channel 50 to the working port B and from there to the annular space 60.
  • the pressure medium displaced from the bottom-side pressure chamber 62 is returned to the tank T via the working port A, the sink module 52 unlocked in the manner described above, the port A "of the directional control valve 44, the tank channel 46 and the return port R.
  • the maximum contact pressure can be set by a suitable setting of the pressure limiting valve 56 is limited to a predetermined value depending on the attachment used or depending on the task at the rear linkage 2.
  • the pressure relief valve 56 can according to Figure 4 a switching valve 140 can be connected upstream or downstream, which can be moved into a throttle position by means of a magnet, so that the pressure medium cannot flow out to the tank via the pressure limiting valve 56.
  • the switching valve 140 is actuated when the contact pressure is to be set to a value which is above the value which can be set on the pressure limiting valve 56 (for example when changing a tire).
  • the rear linkage is operated double-acting.
  • the pressure sensors 124, 126, 130, 132, 134 enable position / traction control, but the function is also ensured without this pressure detection, since protection in the "pressing" working area is possible via the pressure limiting valve 56.
  • the contact pressure / relief pressure can be controlled via the pressure sensors.
  • the safeguarding in the "press" work area then takes place in turn via the pressure limiting valve 56, which can then be set automatically as a function of the support / relief pressure.
  • the rear linkage 2 in the work area "press" should be operated, for example, to pull in a plow.
  • the driver By adjusting the rear operating device 20 or another operating element, the driver generates an actuating signal via which the directional valve 44 moves to one of its lowering positions marked with (a) to the right ( Figure 4 ) is moved.
  • the maximum contact pressure in the working channel 50 is limited by a suitable setting of the pressure limiting valve 56. This maximum contact pressure can vary depending on the attached implement - or as described below - depending on certain operating conditions. It is assumed that the pressure relief valve 56 is set to a pressure of 50 bar.
  • the pressure medium volume flow is conveyed via the working connection B into the annular space 60 of the lifting cylinder 6 and out of the pressure chamber 62 on the bottom side via the activated drain module 52 and the directional control valve 44 returned to the tank T - the rear linkage 2 is lowered and, for example, the plow is retracted.
  • This lowering takes place in accordance with the regulation predetermined via the control unit 16, for example a position regulation.
  • the system is in accordance with Figure 6 initially in the idle state, ie the driver has not yet switched to the "lowering" work area. After switching to lowering, the path and time intervals for motion monitoring are first calculated. There are a multitude of possibilities for this, only two methods being selected as examples.
  • the solution shown is first determined on the basis of the control signal 16 sent from the control valve 16 to the directional valve 44 or the pilot valve 78, the expected normal hoist speed v via a map stored in the memory of the control unit 16. A suitable travel interval dw is calculated from this hoist speed v via a further map. A monitoring time interval dt is then determined from the quotient dw / v.
  • the characteristic maps mentioned are coordinated in such a way that the path interval dw, which is as constant as possible, of about 1/30 of the total stroke results in the main work area "pressing".
  • the control system recognizes that the rear linkage 2 is still lowered. If this moves during the time interval by less than 10% of the calculated travel interval (1/30 of the total stroke), the control system recognizes that the rear linkage 2 "stops" - the directional control valve 44 is placed in its neutral position (0).
  • a switch is made to a motion monitoring mode.
  • a "pressure measurement” is carried out during a predetermined time interval, which does not have to be identical to the time interval described above for the detection of the "stopping" state.
  • the directional control valve 44 is again moved into one of its "lowering" position (a), i.e. a lowering movement is activated via a fixed ramp in order to carry out the "measuring pressure".
  • the rear linkage 2 is lowered and can adapt to the current ground situation.
  • the directional valve 44 is reset to the neutral position (0) - the monitoring is carried out until the lowering signal has been withdrawn via the operating device 20.
  • the time and distance intervals are determined from characteristic fields.
  • the hoist speed can also be used, which is already detected in the course of the electro-hydraulic control (for example via the sensor 30).
  • a "stop" of the rear linkage 2 is recognized when the lowering speed falls below a minimum speed during a predetermined time interval. I.e. Instead of the travel interval, the hoist speed is evaluated directly.
  • the rear linkage can also be operated single-acting.
  • the pressure of the pressure limiting valve 56 is set to a minimum value, for example 5 to 8 bar, so that a minimum pressure is set at the working port B and thus in the annular space 60 of the lifting cylinder 6.
  • a lowering signal is now sent via the electro-hydraulic hoist control (EHR) and the above-mentioned movement monitoring is activated, since the actual change in the travel of the hoist (lifting shaft angle) is less than 10% of the expected change in travel per unit of time (or the hoist speed is below the limit value)
  • the directional control valve 44 is not set to the neutral position (0) as in the double-acting function, but to the floating position (c) - the hoist can adapt to any unevenness in the floor.
  • the behavior set corresponds to that of conventional single-acting hoist valves.
  • a rapid retraction switch is actuated so that the rear linkage is lowered in a double-acting manner at maximum speed until the contact pressure set on the pressure relief valve 56 is reached.
  • the directional valve 44 is not switched to its neutral position (0), but remains in its lowering position (a), so that the rear linkage 2 can immediately follow a further lowering movement.
  • the directional control valve 44 is moved into its neutral position (0) in order to avoid unnecessary heating of the pressure medium.
  • the pump of the working hydraulics may be in the saturation range, i.e. under certain circumstances no other consumer can be operated.
  • the pressure relief valve - preferably automatically - is set to a comparatively low pressure of, for example, 5 bar.
  • the rear linkage 2 is lifted at a fixed load-compensated speed, the speed after a ramp being able to be increased as a function of the path. In this operating mode, a sensitive coupling / uncoupling of the attachments is possible. The empty hoist can be lowered quickly.
  • the pressure of the pressure relief valve 56 must be increased, this mode being able to be set only after a few inquiries, so that there is a deliberate operating restriction.
  • These safety queries can be used, for example, to check whether the handbrake is applied, the required pressure at the pressure relief valve (250 bar) is set, or the switching valve 140 is shifted into its blocking position if the maximum pressure of the pressure relief valve 56 is not sufficient (50 bar).
  • the rear hoist 2 can be controlled with a high degree of precision and operational safety in the “pressing” working area with very little control and device engineering effort.
  • Pressure relief valve can be used, but this is accompanied by a loss of comfort.
  • a hoist valve arrangement for controlling a double-acting hoist or an attachment with a continuously adjustable directional valve and an individual pressure compensator, via which a pressure medium volume flow to and from a lifting cylinder of the hoist can be controlled.
  • a proportionally adjustable pressure relief valve is provided, by means of which the pressure in this area can be limited to a maximum value.
  • the pressure relief valve is preferably set as a function of the operating conditions of the hoist or the type of attachment.

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  • 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)
  • Mechanically-Actuated Valves (AREA)

Claims (10)

  1. Système de vannes pour mécanisme de levage (14), destiné à activer un mécanisme de levage (2, 4) à double effet ou un outil porté en particulier d'un véhicule utilitaire agricole, comportant un distributeur (44) réglable en continu, formant un obturateur de dosage, auquel est associée une balance de pression individuelle (42), par laquelle passe un débit volumétrique de fluide sous pression circulant vers un raccord de travail (A, B), le fluide sous pression, renvoyé via un autre raccord de travail (A, B), étant évacué via le distributeur (44) vers un raccord basse pression ou raccord de cuve (T), et comportant un limiteur de pression (56), qui est monté dans une conduite de travail (48, 50) entre le distributeur (44) et le raccord de travail (A, B), caractérisé en ce que le limiteur de pression (56) est configuré de manière réglable à commande proportionnelle de telle sorte que la pression dans la conduite de travail (48, 50) peut être limitée à différentes valeurs maximales en fonction des différents états de fonctionnement, le distributeur (44) pouvant être réglé, après l'activation du limiteur de pression (56), par l'intermédiaire d'un dispositif de commande (16) dans une position neutre (0) ou une position flottante (c), la pression maximale étant ajustable différemment en fonction des différents générateurs de valeur de consigne / éléments de consigne (18, 20, 24).
  2. Système de vannes pour mécanisme de levage selon la revendication 1, dans lequel le limiteur de pression (56) est configuré de telle sorte qu'il peut être agencé au niveau d'une conduite de travail (50), reliée à la chambre de pression (60), active dans le sens « abaisser », du mécanisme de levage (2, 4) ou de l'outil porté.
  3. Système de vannes pour mécanisme de levage selon la revendication 1 ou 2, dans lequel le limiteur de pression (56) peut être réglé à des valeurs entre 0 et 250 bars.
  4. Système de vannes pour mécanisme de levage selon l'une quelconque des revendications précédentes, dans lequel dans l'autre conduite de travail (48) est agencé un limiteur de pression secondaire (58).
  5. Système de vannes pour mécanisme de levage selon l'une quelconque des revendications précédentes, dans lequel dans les conduites de travail (48, 50) est agencé respectivement un module d'abaissement (52, 54) pour arrêter le fluide de pression sans retour de fuite.
  6. Système de vannes pour mécanisme de levage selon la revendication 5, dans lequel le module d'abaissement (52, 54) est réalisé sous la forme d'une balance de pression d'écoulement, qui peut être réglée dans une position d'écoulement par une pression de commande.
  7. Système de vannes pour mécanisme de levage selon l'une quelconque des revendications précédentes, dans lequel la balance de pression individuelle (42) est montée en amont du distributeur (44) et est sollicitée dans le sens d'ouverture par la pression de charge (LS) la plus élevée et par la force d'un ressort (70) de la balance de pression, et dans le sens de fermeture par la pression en amont du distributeur (44).
  8. Système de vannes pour mécanisme de levage selon l'une quelconque des revendications précédentes, comportant une sortie d'urgence (100) actionnable manuellement, laquelle permet de commander l'ouverture d'une liaison de la conduite de travail (48, 50), parcourue par le fluide sous pression, avec la cuve (T).
  9. Système de vannes pour mécanisme de levage selon l'une quelconque des revendications précédentes, qui est configuré de telle sorte qu'il peut être utilisé pour commander un mécanisme de levage arrière (2) ou un mécanisme de levage avant (4) d'un tracteur (1).
  10. Système de vannes pour mécanisme de levage selon l'une quelconque des revendications précédentes, comportant une vanne de commande (140) montée en amont du limiteur de pression (56).
EP05772453.6A 2004-07-09 2005-07-06 Systeme de soupapes de mecanisme de levage Expired - Lifetime EP1766146B2 (fr)

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DE102004033315A DE102004033315A1 (de) 2004-07-09 2004-07-09 Hubwerksventilanordnung
PCT/EP2005/007308 WO2006005496A1 (fr) 2004-07-09 2005-07-06 Systeme de soupapes de mecanisme de levage

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WO (1) WO2006005496A1 (fr)

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US8020485B2 (en) 2011-09-20
ATE524617T1 (de) 2011-09-15
DE102004033315A1 (de) 2006-02-09
WO2006005496A1 (fr) 2006-01-19
US20070277519A1 (en) 2007-12-06
EP1766146B1 (fr) 2011-09-14
EP1766146A1 (fr) 2007-03-28

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