EP1766146B2 - Lifting gear valve arrangement - Google Patents
Lifting gear valve arrangement Download PDFInfo
- 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
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- 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.)
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- 238000010438 heat treatment Methods 0.000 description 1
- 238000010079 rubber tapping Methods 0.000 description 1
Images
Classifications
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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
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- 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
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- 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
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- 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
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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
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
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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
- F15B11/08—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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/57—Control of a differential pressure
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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
- 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
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
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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
- 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
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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
- 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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Abstract
Description
Die Erfindung betrifft eine Hubwerksventilanordnung zur Ansteuerung eines doppeltwirkenden Hubwerks oder eines Anbaugerätes eines mobilen Arbeitsgerätes gemäß dem Oberbegriff des Patentanspruches 1. Eine solche Anordnung ist aus der
In modernen Traktoren der mittleren und oberen Leistungsklasse kommen bei der Arbeitshydraulik zunehmend elektrisch ansteuerbare Wegeventile für die Steuerung von Arbeitsfunktionen angekoppelter Geräte zum Einsatz. Die Steuerung dieser hydraulischen Funktionen erfolgt über einen sehr kompakten Steuerblock, bei dem die Steuerung mit allen wesentlichen Wege- und Regelventilen zu einer Einheit zusammengefasst sind. Ein derartiger Steuerblock ist beispielsweise in dem Katalog 1 987 760 507 (elektronisch-hydraulische Hubwerksregelung für Traktoren) der Anmelderin beschrieben.In modern tractors in the medium and upper performance class, electrically controllable directional control valves are increasingly being used in work hydraulics for controlling work functions of connected devices. These hydraulic functions are controlled via a very compact control block, in which the control system with all essential directional and control valves is combined into one unit. Such a control block is described, for example, in the applicant's
Zur Erfassung der auftretenden Kräfte, Drücke, Geschwindigkeiten und Hubwerkspositionen sind am Traktor 1 noch eine Vielzahl von Sensoren, beispielsweise Drucksensoren 26, Drehzahlsensoren 28, Lagesensoren 30, Kraftsensoren 32 oder Geschwindigkeitssensoren 34 vorgesehen, deren Signale über das Steuergerät 16 verarbeitbar sind.A plurality of sensors, for
Wie bereits erwähnt, ist bei den meisten bekannten Lösungen das Heckhubwerk 2 einfachwirkend ausgeführt, wobei der Hubzylinder 6 durch Druckmittelzufuhr über die Pumpe 12 ausgefahren wird und das Absenken durch das Eigengewicht des Heckhubwerks 2 und des daran ggf. angebauten Gerätes wie beispielsweise eines Pflugs 36 erfolgt.As already mentioned, in most known solutions the
Beispielsweise zum Säen mit einer Drillmaschine wird das Heckhubwerk 2 in eine Schwimmstellung gebracht, so dass das Anbaugerät aufgrund seines Eigengewichtes auf dem Boden aufliegt und eventuelle Bodenunebenheiten überfährt.For example, for sowing with a seed drill, the
Mit den herkömmlichen einfachwirkenden Heckhubwerken lässt sich der Auflagedruck jedoch nicht aktiv verändern, da diese Hubwerke nicht im Arbeitsbereich "Drücken" betrieben werden können. Hierzu sind doppeltwirkende Heckhubwerke erforderlich, deren Grundaufbau demjenigen der üblicher Weise verwendeten doppeltwirkenden Fronthubwerke entspricht. Die doppeltwirkenden Heckhubwerke 2 ermöglichen es, den Hubzylinder 6 in Richtung "Drücken" anzusteuern, so dass beispielsweise ein aktives Pflugeinziehen ermöglicht ist. Dieser Betriebszustand kann zum Beispiel auch verwendet werden, um den Traktor zum Wechsel der hinteren, großen Räder rückseitig anzuheben, so dass er auf der pendelnden Vorderachse und auf dem vom Heckhubwerk betätigten Anbaugerät oder direkt auf den Unterlenkern steht.However, 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. This requires double-acting rear linkages, the basic structure of which corresponds to that of the double-acting front linkages normally used. The double-acting
Der bisher eingesetzte Drucksensor beispielsweise im Fronthubwerk ist auf der Tragen-Seite angeordnet, es erfolgt eine Entlastungsdruckregelung - der Auflagedruck bleibt unbekannt oder wird zur Regelung nicht verwendet.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.
Demgegenüber liegt der Erfindung die Aufgabe zugrunde, eine Hubwerksventilanordnung zu schaffen, die es ermöglicht, mit minimalem Aufwand einen Auflagedruck einzustellen und zu begrenzen.In contrast, 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.
Diese Aufgabe wird durch eine Hubwerksventilanordnung mit den Merkmalen des Patentanspruches 1 gelöst.This object is achieved by a hoist valve arrangement with the features of
Erfindungsgemäß hat die Hubwerksventilanordnung ein stetig verstellbares Wegeventil, dem eine oder mehrere Druckwaagen vor- oder nachgeschaltet sind. Zwei Arbeitsanschlüsse der Hubwerksventilanordnung sind mit den in Heben- bzw. Senkenrichtung wirksamen Druckräumen des Hubwerks - oder genauer gesagt des Hubzylinders des Hubwerks - verbunden. Erfindungsgemäß ist in einer Arbeitsleitung ein proportional verstellbares Druckbegrenzungsventil vorgesehen, über das der Druck in dieser Arbeitsleitung auf einen veränderbaren Maximalwert begrenzbar ist. Erfindungsgemäß wird der Druck in dieser Arbeitsleitung über das Druckbegrenzungsventil in Abhängigkeit von bestimmten Betriebszuständen begrenzt, so dass entsprechend der Auflagedruck variabel einstellbar ist.According to the invention, 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. According to the invention, 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. According to the invention, 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.
Unter dem Begriff Hubwerk ist dabei allgemein eine Vorrichtung zu verstehen, über die ein einem mobilen Arbeitsgerät zugeordnetes Arbeitswerkzeug, Anbaugerät oder dergleichen gegenüber einer Bezugsebene bewegbar oder gegen diese drückbar ist.The term 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.
Diese sehr einfach aufgebaute Hubwerksventilanordnung ermöglicht es, den Auflagedruck durch Ansteuerung des Druckbegrenzungsventils auf äußerst einfache und kostengünstige Weise an unterschiedliche Betriebsbedingungen anzupassen.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.
Bei einem bevorzugten Ausführungsbeispiel der Erfindung lässt sich der Maximaldruck über das Druckbegrenzungsventil in einem Bereich zwischen 0 bis 250 bar verstellen. Bei der Einstellung eines minimalen Auflagedrucks (beispielsweise 5 bis 8 bar) kommt die Funktion des mit der erfindungsgemäßen Hubwerksventilanordnung ausgeführten Hubwerks derjenigen eines einfachwirkenden Hubwerks gleich. Im Normalbetrieb stellt der Fahrer das Druckbegrenzungsventil auf seinen Maximalwert ein, so dass der Auflagedruck entsprechend einen maximalen Wert erreichen kann.In a preferred embodiment of the invention, the maximum pressure can be set via the pressure relief valve in a range between 0 to Adjust 250 bar. When a minimum contact pressure (for example 5 to 8 bar) is set, 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. In normal operation, the driver sets the pressure relief valve to its maximum value so that the contact pressure can correspondingly reach a maximum value.
Die Einstellung des Maximaldrucks erfolgt erfindungsgemäß in Abhängigkeit von unterschiedlichen Betriebszuständen - beispielsweise beim Anheben der Hinterachse für den Reifenwechsel, bei Betätigung eines Schnelleinzugsschalters für eine schnellste Senkenbewegung, bei Betätigung des Hecktasters, etc., wobei jeweils geeignete Maximaldrücke eingestellt werden. Im Normalbetrieb stellt der Fahrer den Maximaldruck ein.According to the invention, 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. In normal operation, the driver sets the maximum pressure.
Bei der erfindungsgemäßen Hubwerksventilanordnung erfolgt die Ansteuerung erfindungsgemäß über ein Steuergerät, über das das stetig verstellbare Wegeventil nach Ansprechen des Druckbegrenzungsventils in eine Neutralstellung (dw) oder in eine Schwimmstellung (ew) verstellbar ist.In the hoist valve arrangement according to the invention, 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.
Bei einem besonders bevorzugten Ausführungsbeispiel ist zur Begrenzung des Drucks in der anderen Arbeitsleitung, d.h. vorzugsweise in der mit dem in Richtung "Heben" wirksamen Druckraum verbundenen Arbeitsleitung ein Sekundärdruckbegrenzungsventil vorgesehen.In a particularly preferred embodiment, to limit the pressure in the other working line, i.e. a secondary pressure relief valve is preferably provided in the working line connected to the pressure chamber acting in the "lifting" direction.
In den Arbeitsleitungen ist stromabwärts der beiden Ausgangsanschlüsse des stetig verstellbaren Wegeventils jeweils ein Senkenmodul vorgesehen, das in einer Grundposition als entsperrbares Rückschlagventil wirkt und bei Beaufschlagung mit einem Steuerdruck als Ablaufdruckwaage wirkt.In the working lines, 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.
Die erfindungsgemäße Hubwerksventilanordnung ist vorzugsweise als LS-System ausgebildet, wobei die Druckwaage als Individualdruckwaage ausgebildet ist, der ein eine veränderliche Messblende ausbildendes stetig verstellbares Wegeventil nachgeschaltet ist. Die Druckwaage ist in Öffnungsrichtung vom höchsten Lastdruck der angesteuerten Verbraucher beaufschlagt. Dieser höchste Lastdruck wird auch an eine Pumpe gemeldet und diese so geregelt, dass in der Pumpenleitung ein um eine vorbestimmte Druckdifferenz oberhalb des Lastdrucks liegender Pumpendruck anliegt.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.
Die Hubwerksventilanordnung kann mit einem von Hand betätigbaren Notablass ausgeführt werden, über den die den höheren Druck führende Arbeitsleitung mit dem Tank verbindbar ist.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.
Die erfindungsgemäße Lösung wird vorzugsweise bei einem Heckhubwerk eines Traktors eingesetzt. Denkbar ist aber auch ein Einsatz bei Anbaugeräten, beispielsweise Pflügen und außerhalb landtechnischer Anwendungen, beispielsweise zum Betätigen von Schilden, wie sie beispielsweise bei Schneeräumern zum Einsatz kommen.The solution according to the invention is preferably used in a rear linkage of a tractor. However, it is also conceivable to use it with attachments, for example plowing and outside agricultural applications, for example for actuating shields, as are used, for example, in snow clearers.
Sonstige vorteilhafte Weiterbildungen der Erfindung sind Gegenstand weiterer Unteransprüche.Other advantageous developments of the invention are the subject of further dependent claims.
Im Folgenden werden bevorzugte Ausführungsbeispiele der Erfindung anhand schematischer Zeichnungen näher erläutert. Es zeigen:
-
ein Grundschema der Arbeitshydraulik eines herkömmlichen Traktors;Figur 1 -
eine Schemadarstellung unterschiedlicher Betriebszustände eines doppeltwirkenden Heckhubwerks, das mit einer erfindungsgemäßen Hubwerksventilanordnung ausgeführt ist;Figur 2 -
einen Hydraulikschaltplan des Heckhubwerks, mit dem die Betriebszustände gemäßFigur 3 einstellbar sind;Figur 2 -
eine Detaildarstellung der Hubwerksventilanordnung ausFigur 4 ;Figur 3 -
Figur 5 eine Schnittdarstellung einer Hubwerksventilanordnung, die in der Schaltung gemäß verwendet ist undFigur 3 -
ein Diagramm zur Verdeutlichung der Steuerungsstruktur zur Ansteuerung der Hubwerksventilanordnung ausFigur 6 .Figur 3
-
Figure 1 a basic diagram of the working hydraulics of a conventional tractor; -
Figure 2 a schematic representation of different operating states of a double-acting rear linkage, which is designed with a linkage valve arrangement according to the invention; -
Figure 3 a hydraulic circuit diagram of the rear linkage, with which the operating conditions accordingFigure 2 are adjustable; -
Figure 4 a detailed representation of the hoist valve arrangementFigure 3 ; -
Figure 5 a sectional view of a hoist valve assembly, according to the circuitFigure 3 is used and -
Figure 6 a diagram to illustrate the control structure for controlling the hoist valve arrangementFigure 3 .
Es sei angenommen, dass der in
Ein Heckhubwerk 2 gemäß
In
Wie eingangs erwähnt, kann zum Einstellen des Arbeitsbereiches "Drücken" das Heckhubwerk 2 so angesteuert werden, dass eine in Richtung auf den Boden wirkende Druckkraft aufgebracht wird. Eine derartige Einstellung ist beispielsweise beim aktiven Pflugeinziehen oder bei einem Packer erforderlich. Im Arbeitsbereich "Drücken" kann auch die Hinterachse des Traktors 1 angehoben werden, so dass ein Reifenwechsel möglich ist.As mentioned at the beginning, the
Durch die im Folgenden näher beschriebene Hubwerksventilanordnung 14 kann die im Arbeitsbereich "Drücken" wirksame Druckkraft auf unterschiedliche Werte begrenzt werden, wobei dieser Grenzwert in Abhängigkeit von im Folgenden noch näher beschriebenen Betriebszuständen variiert wird.By means of the hoist
In
Der Druckanschluss P ist über einen Zulaufkanal 40 mit einem Eingangsanschluss P' einer Individualdruckwaage 42 verbunden, deren Ausgangsanschluss A' mit einem Eingangsanschluss P" eines stetig verstellbaren Wegeventils 44 verbunden ist. Dessen Rücklaufanschluss R ist über einen Rücklaufkanal 46 mit dem Tankanschluss T der Hubwerksventilanordnung 14 verbunden. Das Wegeventil 44 hat zwei Arbeitsanschlüsse A" und B", die über Arbeitskanäle 48, 50 mit den beiden Arbeitsanschlüssen A, B der Hubwerksventilanordnung 14 verbunden sind.The pressure port P is connected via an
In jedem Arbeitskanal 48, 50 ist jeweils ein Senkenmodul 52, 54 vorgesehen, das in einer Grundstellung als entsperrbares Rückschlagventil zur leckölfreien Einspannung des Hubzylinders 6 des Heckhubwerks 2 dient und in einer Regelposition den vom Hubzylinder 6 zurückströmenden Druckmittelvolumenstrom im Sinne einer Ablaufregelung steuert.A lowering
Der Arbeitskanal 50 ist stromabwärts des Senkenmoduls 54 über ein vorgesteuertes proportional verstellbares Druckbegrenzungsventil 56 mit dem Tankanschluss T verbindbar. Der Druck im anderen Arbeitskanal 48 wird über ein Sekundär-druckbegrenzungsventil 58 begrenzt. Der Hubzylinder 6 ist - wie erwähnt - doppeltwirkend ausgeführt, wobei ein in Richtung "Senken" wirksamer Ringraum 60 mit dem Arbeitsanschluss B und der in Richtung "Heben" wirksame Druckraum 62 mit dem Arbeitsanschluss A der Hubwerksventilanordnung 14 verbunden ist. Über den Hubzylinder 6 werden ein schwenkbar an einer Hubwelle 64 gelagerter Arm 66 sowie weitere Koppelelemente betätigt, an denen beispielsweise ein Anbaugerät, wie eine Drillmaschine oder ein Pflug 68 angebaut ist.The working
Einzelheiten der Hubwerksventilanordnung 14 werden anhand der vergrößerten Darstellung in
Ein Druckwaagenkolben 69 der Druckwaage 42 ist von einer Druckwaagenfeder 70 sowie von dem über einen Kanal 72 von einem mit dem LS-Anschluss verbundenen Lastmeldekanal 74 abgegriffenen Druck in Öffnungsrichtung und von dem Druck in einem Steuerkanal 76 in Schließrichtung beaufschlagt, der zwischen der Druckwaage 42 und dem Wegeventil 44 vom Zulaufkanal 40 abzweigt. Der LS-Kanal 74 führt zu einem Steueranschluss LS" des Wegeventils 44. Dieses hat noch zwei weitere Steueranschlüsse X, denen ausgangsseitig Steueran-schlüsse XA und XB zugeordnet sind.A
Die Betätigung des Wegeventils 44 erfolgt über ein in
Die Ventilkörper der beiden Senkenmodule 52, 54 werden jeweils durch eine Feder 88 und durch den am Ausgang A" bzw. B" über Druckwaagenkanäle 90, 92 abgegriffenen individuellen Lastdruck stromabwärts des Wegeventils 44 in ihre Grundposition (a) beaufschlagt, in der die Senken-module 52, 54 als Rückschlagventile wirken, die eine Druckmittelströmung zu den Anschlüssen A, B zulassen. In Öffnungsrichtung sind die Ventilkörper der Senkenmodule 52, 54 jeweils von dem am Anschluss XA bzw. XB anliegenden Steuerdruck beaufschlagt, der über einen Entsperrkanal 94, 96 abgegriffen wird. Dieser Steuerdruck kann beispielsweise dem Eingangsdruck der Pilotventilanordnung 78 entsprechen.The valve bodies of the two
Der Aufbau der Hubwerksventilanordnung mit der Individualdruckwaage 42, dem stetig verstellbaren Wegeventil 44 und dem beiden nachgeordneten Senkenmodulen 52, 54 entspricht im wesentlichen der herkömmlichen Lösung des Ventils SB23 LS, so dass in der Folge nur die zum Verständnis der Erfindung wesentlichen Elemente beschrieben werden und im übrigen diesbezüglich auf den vorhandenen Stand der Technik zum Wegeventil SB23 LS verwiesen wird.The structure of the hoist valve arrangement with the
Soll beispielsweise der Hubzylinder 6 zum Anheben des Pflugs 68 verfahren werden, so wird über die Pilotventilanordnung 78 der Ventilschieber 80 des Wegeventils 44 in eine seiner mit (b) gekennzeichneten Regelpositionen verschoben. Je nach Position wird dabei eine Messblende aufgesteuert, die der Individualdruckwaage 42 nachgeschaltet ist. In Abhängigkeit von der Messblendenöffnung stellt sich die Druckwaage 42 in eine Regelposition ein, in der der Druckabfall über der Messblende konstant gehalten und somit ein lastdruckunabhängiger Druckmittelvolumenstrom eingestellt ist. Dieser Druckmittelvolumenstrom wird in den mit (b) gekennzeichneten Regelpositionen über die Druckwaage 42, den Druckanschluss P" und den Ausgangsanschluss A" des Wegeventils 44 zum Eingangsanschluss PDW des Senkenmoduls 52 und über dessen Ausgangsanschluss ADW zum Arbeitsanschluss A der Hubwerksventilanordnung 14 und von dort in den bodenseitigen Druckraum 62 geführt - der Hubzylinder 6 fährt aus. Das aus dem Ringraum 60 verdrängte Druckmittel strömt über den Arbeitsanschluss B der Hubwerksventilanordnung 14, den Arbeitskanal 50, den Ausgangsanschluss BDW und den Eingangsanschluss PDW des Senkenmoduls 54 zum Anschluss B" des Wegeventils 44 und von dort über den Rücklaufanschluss R, den Tankkanal 46 und den Tankanschluss T zurückzum Tank. Diese Rückströmung wird dadurch ermöglicht, dass der an der Pilotventilanordnung 78 anliegende Eingangsdruck über den Steueranschluss X und den Ausgangsanschluss XB des Wegeventils 44 abgegriffen und über den Entsperrkanal 96 den Ventilkörper in Öffnungsrichtung beaufschlagt, so dass der Senkenmodul 54 entsperrt und die Rückströmung des Druckmittels zum Tank T hin ermöglicht. In diesen mit (b) gekennzeichneten Positionen des Senkenmoduls 54 wirkt dieser als Ablaufdruckwaage, über die der ablaufende Druckmittelvolumenstrom in gewissem Umfang geregelt wird.If, for example, the
Zum Andrücken eines vom Hubwerk getragenen Anbaugerätes wird das Wegeventil 44 in eine seiner mit (a) gekennzeichneten Regelpositionen verschoben, so dass entsprechend die Druckmittelzufuhr über das Senkenmodul 54 in seiner Rückschlagfunktion zum Ringraum 60 erfolgt, während das aus dem bodenseitigen Druckraum 62 abströmende Druckmittel über das entsperrte Senkenmodul 52 und das Wegeventil 44 zum Tank hin abströmt. Das Entsperren erfolgt dabei über den Steuerdruck, der über die Steueranschlüsse X, XA des Wegeventils 44 und den Entsperrkanal 94 an die in Öffnungsrichtung wirksame Steuerfläche des Senkenmoduls 52 geführt ist.To press on an attachment carried by the lifting mechanism, the
Zum lastfreien Auflegen wird das Wegeventil 44 in seine Schwimmstellung (Endstellung c) verfahren, in der beide Senkenmodule 52, 54 entsperrt und in ihre mit (b) gekennzeichnete Durchgangsposition verfahren werden und die Arbeitsanschlüsse A, B und der Steueranschluss LS mit dem Tankanschluss T verbunden und der Eingangsanschluss P" abgesperrt ist.For load-free placement, the
In dem Arbeitsbereich "Drücken" wird - wie im Folgenden noch ausführlich erläutert - der Maximaldruck im Arbeitskanal 50 durch geeignete Einstellung des proportional verstellbaren Wegeventils 44 auf eine Wert von beispielsweise zwischen 0 bis 250 bar begrenzt.In the "press" working area, as will be explained in detail below, the maximum pressure in the working
Die in
Bei der in
Über das Sekundärdruckbegrenzungsventil 58 wird der Druck im Arbeitskanal 48 (Anschluss A) auf einen unterhalb des Pumpendrucks eingestellten Maximaldruck begrenzt. Der Aufbau derartiger Sekundärdruckbegrenzungsventile ist bekannt, so dass weitere Erläuterungen entbehrlich sind. Auch der Aufbau des vorgesteuerten proportional verstellbaren Druckbegrenzungsventils 56 ist per se bekannt - ein Kolben 108 des Druckbegrenzungsventils 56 ist über eine schwache Druckfeder 110 und durch den Druck im Federraum gegen einen Ventilsitz in eine Schließstellung belastet. Der Druck im Federraum ist durch die mittels eines Proportionalmagneten 112 auf einen Schließkegel 114 aufgebrachte Kraft begrenzt.Via the secondary
Die Ansteuerung des Proportionalmagneten 112 erfolgt in der nachfolgend beschriebenen Weise über das Steuergerät 16.The
Die Heben- und Senkenmodule 52, 54 haben ebenfalls einen herkömmlichen Aufbau, wobei ein Modulkolben 116 über eine Schließfeder 118 in eine Schließstellung vorgespannt ist. Der Federraum der Schließfeder 118 ist in der Schließstellung des Modulkolbens 116 vom Druck im Arbeitskanal 48 bzw. 50 beaufschlagt. Im Boden des Modulkolbens 116 ist ein Vorsteuerventilkörper 120 angeordnet, der ebenfalls über die Schließfeder 118 in seine Schließposition vorgespannt ist und dabei eine Vorsteueröffnung verschliesst. Der Vorsteuerventilkörper 120 hat einen Vorsprung, der in Anlage an einen Aufstoßkolben 122 bringbar ist. Dieser Aufstoßkolben ist rückseitig mit dem Druck am Steueranschluss XA (XB) beaufschlagbar, der über das Wegeventil 54 und dessen Anschluss X abgreifbar ist. D.h. bei Beaufschlagung des Aufstoßkolbens 122 des Senkenmoduls 52 oder 54 wird der Vorsteuerventilkörper 120 gegen die Kraft der Schließfeder 118 von seinem Vorsteuersitz angehoben - der Modulkolben 116 ist dann druckausgeglichen und kann durch den Aufstoßkolben 122 gegen die Kraft der Schließfeder 118 von seinem Sitz abgehoben werden, so dass Druckmittel vom Arbeitsanschluss A bzw. B zum Tank T hin abströmen kann.The lifting and lowering
Mit den Bezugszeichen 124, 126, 130, 132, 134 sind Drucksensoren bezeichnet, über die die Drücke in den Arbeitskanälen 48, 50, der Druck am Druckanschluss P, der Lastdruck und sonstige Drücke erfassbar sind.
Das Pilotventil 78 gemäß
Da - wie gesagt - der Grundaufbau der Hubwerksventilanordnung 14 gemäß
Zum Einstellen des Betriebsbereiches "Drücken" wird das Pilotventil 78 so angesteuert, dass in den Steuerräumen 136, 138 eine Steuerdruckdifferenz wirkt, durch die der Ventilschieber 80 aus der in
Dem Druckbegrenzungsventil 56 kann gemäß
Im Folgenden wird das Steuerkonzept der Hubwerksansteuerung anhand unterschiedlicher Betriebszustände erläutert.The control concept of the hoist control is explained below on the basis of different operating states.
In der Regel wird das Heckhubwerk doppeltwirkend betrieben. Die Drucksensoren 124, 126, 130, 132, 134 ermöglichen dabei eine Lage-/Zugkraftregelung, wobei die Funktion jedoch auch ohne diese Druckerfassung gewährleistet ist, da eine Absicherung im Arbeitsbereich "Drücken" über das Druckbegrenzungsventil 56 möglich ist. Bei Einsatz der in
Es sei angenommen, dass das Heckhubwerk 2 im Arbeitsbereich "Drücken" (siehe
Das System befindet sich gemäß
In dem Fall, in dem weiterhin von der elektrohydraulischen Hubwerksregelung ein Senken-Sollsignal anliegt (Solllage noch nicht erreicht) und - wie vorstehend beschrieben - die Senkenbewegung abgeschaltet ist (Wegeventil 44) in Neutralstellung (0)) wird auf einen Bewegungsüberwachungsmodus umgeschaltet. Dazu wird während eines vorbestimmten Zeitintervalls, der nicht mit dem eingangs beschriebenen Zeitintervall zur Erfassung des Zustands "Stehenbleiben" identisch sein muss, eine "Druckmessung" durchgeführt. Dazu wird das Wegeventil 44 wieder in eine seiner "Senken"-Position (a) verstellt, d.h., es wird eine Senkenbewegung über eine festgelegte Rampe aktiviert um das "Druck messen" vorzunehmen. Dadurch wird das Heckhubwerk 2 abgesenkt und kann sich an die aktuelle Bodensituation anpassen. Nach dieser Senkenbewegung wird das Wegeventil 44 wieder in die Neutralstellung (0) zurückgestellt - die Überwachung wird solange durchgeführt, bis über das Bediengerät 20 das Senken-signal zurückgenommen ist.In the event that a lowering target signal is still present from the electrohydraulic hoist control (target position has not yet been reached) and - as described above - the lowering movement is switched off (directional valve 44) in neutral position (0)), a switch is made to a motion monitoring mode. For this purpose, 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. For this purpose, the
In dem Fall, in dem eine Hubwerksbewegung nach oben aufgrund äußerer Kräfte erfolgt (beispielsweise Überfahren einer Bodenunebenheit, wird die vorbeschriebene erneute Absenkbewegung unmittelbar nach Auftreten dieser nach oben gerichteten Hubwerksbewegung gestartet, wobei diese unabhängig von dem eingestellten Zeitintervall (beispielsweise 5 Sekunden) erfolgen kann. Nach Zurücknehmen des Senkensignals befindet sich das System wieder in seinem in
Bei dem vorbeschriebenen Steuerungskonzept werden die Zeit- und Wegintervalle aus Kennlinienfeldern bestimmt. Bei einer vereinfachten Lösung kann anstelle dieses relativ aufwendigen Verfahrens zur Ermittlung der Zeit-/Wegintervalle aus Kennlinienfeldern auch die Hubwerksgeschwindigkeit verwendet werden, die ohnehin im Rahmen der elektrohydraulischen Regelung erfasst ist (beispielsweise über den Sensor 30). Ein "Stehenbleiben" des Heckhubwerks 2 wird dann erkannt, wenn die Senkgeschwindigkeit während eines vorbestimmten Zeitintervalls eine Minimalgeschwindigkeit unterschreitet. D.h. anstelle des Wegintervalls wird direkt die Hubwerksgeschwindigkeit ausgewertet.In the control concept described above, the time and distance intervals are determined from characteristic fields. In the case of a simplified solution, instead of this relatively complex method for determining the time / distance intervals 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
Wie erwähnt, kann das Heckhubwerk auch einfachwirkend betrieben werden. Hierzu wird der Druck des Druckbegrenzungsventils 56 auf einen Minimalwert, beispielsweise 5 bis 8 bar eingestellt, so dass am Arbeitsanschluss B und damit im Ringraum 60 des Hubzylinders 6 ein minimaler Druck eingestellt ist. Wird nun über die elektrohydraulische Hubwerksregelung (EHR) ein Senken-Signal abgegeben und die vorbeschriebene Bewegungsüberwachung aktiviert, da die tatsächliche Wegänderung des Hubwerks (Hubwellenwinkel) weniger als 10 % der erwarteten Wegänderung pro Zeiteinheit beträgt (oder die Hubwerksgeschwindigkeit unterhalb des Grenzwerts liegt), so wird das Wegeventil 44 nicht wie in der doppeltwirkenden Funktion in die Neutralstellung (0) sondern in die Schwimmstellung (c) verstellt - das Hubwerk kann sich an eventuelle Unebenheiten des Bodens anpassen. Das eingestellte Verhalten entspricht demjenigen herkömmlicher einfachwirkender Hubwerksventile.As mentioned, the rear linkage can also be operated single-acting. For this purpose, the pressure of the
Zum Betätigen des Schnelleinzugs wird ein Schnelleinzugsschalter betätigt, so dass das Heckhubwerk doppeltwirkend mit maximaler Geschwindigkeit abgesenkt wird, bis der am Druckbegrenzungsventil 56 eingestellte Auflagedruck erreicht ist. Bei Erreichen dieses Auflagedrucks wird im Unterschied zur vorbeschriebenen Grundfunktion das Wegeventil 44 nicht in seine Neutralposition (0) umgeschaltet, sondern verbleibt in seiner Senken-Position (a), so dass das Heckhubwerk 2 sofort einer weiteren Absenkbewegung folgen,kann.To actuate the rapid retraction, 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
Für den Fall, dass der Fahrer den Schnelleinzugsschalter längere Zeit betätigt (länger als beispielsweise 10 Sekunden) und das Heckhubwerk 6 während dieser Zeit stehenbleibt, wird das Wegeventil 44 in seine Neutralposition (0) verstellt, um eine unnötige Druckmittelerwärmung zu vermeiden.In the event that the driver operates the rapid feed switch for a longer time (longer than, for example, 10 seconds) and the
Während der Betätigung in Senkenrichtung befindet sich die Pumpe der Arbeitshydraulik evtl. im Sättigungsbereich, d.h. es kann unter Umständen kein anderer Verbraucher betätigt werden.During the actuation in the lowering direction, the pump of the working hydraulics may be in the saturation range, i.e. under certain circumstances no other consumer can be operated.
Bei der Betätigung des Hecktasters 24 (
Wie eingangs erläutert, ist es beispielsweise zum Reifenwechsel erwünscht, die Traktorhinterachse über das Heckhubwerk 2 anzuheben, so dass der Traktor 1 auf der pendelnden Vorderachse und einem evtl. nicht standfesten Anbaugerät steht, so dass eine erhebliche Kippgefahr besteht. Um diese zu verringern, wird der Maximalauflagedruck auf einen vergleichsweise niedrigen Druck, beispielsweise 50 bar begrenzt - ein Reifenwechsel ist dann ohne weiteres nicht möglich.As explained at the beginning, it is desirable, for example, to change the tires, to lift the rear tractor axle via the
Zum Reifenwechsel muss der Druck des Druckbegrenzungsventils 56 erhöht werden, wobei dieser Modus erst nach einigen Abfragen eingestellt werden kann, so dass bewusste Bedienungseinschränkung vorliegt. Anhand dieser Sicherheitsabfragen kann beispielsweise überprüft werden, ob die Handbremse angezogen ist, der erforderliche Druck am Druckbegrenzungsventil (250 bar) eingestellt ist oder das Schaltventil 140 in seine Sperrstellung verschoben ist, falls der Maximaldruck des Druckbegrenzungsventils 56 nicht ausreichend ist (50 bar).To change the tire, the pressure of the
Durch die vorbeschriebenen Steuerungskonzepte im Zusammenwirken mit der Hubwerksventilanordnung lässt sich mit sehr geringem regelungstechnischen und vorrichtungstechnischen Aufwand das Heckhubwerk 2 im Arbeitsbereich "Drücken" mit hoher Präzision und Betriebssicherheit steuern.Due to the control concepts described above in cooperation with the hoist valve arrangement, 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.
Anstelle des vorbeschriebenen verstellbaren Druckbegrenzungsventils 56 kann auch ein fest eingestelltesInstead of the above-described adjustable
Druckbegrenzungsventil verwendet werden, womit allerdings eine Komforteinbuße einher geht.Pressure relief valve can be used, but this is accompanied by a loss of comfort.
Offenbart ist eine Hubwerksventilanordnung zur Ansteuerung eines doppeltwirkenden Hubwerks oder eines Anbaugerätes mit einem stetig verstellbaren Wegeventil und einer Individualdruckwaage, über die ein Druckmittelvolumenstrom zu und von einem Hubzylinder des Hubwerks steuerbar ist. Im Druckmittelströmungspfad zwischen einem Ausgangsanschluss des Wegeventils und einem Arbeitsanschluss der Hubwerksventilanordnung ist ein proportional verstellbares Druckbegrenzungsventil vorgesehen, über das der Druck in diesem Bereich auf einen Maximalwert begrenzbar ist. Die Einstellung des Druckbe-grenzungsventils erfolgt vorzugsweise in Abhängigkeit von den Betriebszuständen des Hubwerks oder der Art des Anbaugerätes.Disclosed is 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. In the pressure medium flow path between an outlet connection of the directional control valve and a working connection of the hoist valve arrangement, 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.
- 11
- Traktortractor
- 22nd
- HeckhubwerkRear linkage
- 44th
- FronthubwerkFront linkage
- 66
- HubzylinderLifting cylinder
- 88th
- HubzylinderLifting cylinder
- 1010th
- SteuerblockControl block
- 1212th
- Pumpepump
- 1414
- HubwerksventilanordnungHoist valve arrangement
- 1616
- SteuergerätControl unit
- 1818th
- BediengerätControl unit
- 2020th
- BediengerätControl unit
- 2222
- Kabinecabin
- 2424th
- HecktasterRear button
- 2626
- DrucksensorPressure sensor
- 2828
- DrehzahlsensorSpeed sensor
- 3030th
- LagesensorPosition sensor
- 3232
- KraftsensorForce sensor
- 3434
- GeschwindigkeitssensorSpeed sensor
- 3636
- AnbaugerätAttachment
- 3838
- VerstellpumpeVariable pump
- 4040
- ZulaufkanalInlet channel
- 4242
- DruckwaagePressure compensator
- 4444
- WegeventilDirectional control valve
- 4646
- TankkanalTank channel
- 4848
- ArbeitskanalWorking channel
- 5050
- ArbeitskanalWorking channel
- 5252
- SenkenmodulSink module
- 5454
- SenkenmodulSink module
- 5656
- DruckbegrenzungsventilPressure relief valve
- 5858
- SekundärdruckbegrenzungsventilSecondary pressure relief valve
- 6060
- RingraumAnnulus
- 6262
- DruckraumPressure room
- 6464
- HubwelleLifting shaft
- 6666
- Armpoor
- 6868
- AnbaugerätAttachment
- 6969
- DruckwaagenkolbenPressure balance piston
- 7070
- DruckwaagenfederPressure balance spring
- 7272
- Kanalchannel
- 7474
- LS-KanalLS channel
- 7575
- VorsteuerelementPilot control
- 7676
- SteuerkanalControl channel
- 7777
- VorsteuerelementPilot control
- 7878
- PilotventilanordnungPilot valve arrangement
- 7979
- SteuerölversorgungTax oil supply
- 8080
- VentilschieberValve spool
- 8282
- SteuerleitungControl line
- 8484
- SteuerleitungControl line
- 8686
- RückstellfederanordnungReturn spring arrangement
- 8888
- Federfeather
- 9090
- DruckwaagenkanalPressure compensator channel
- 9292
- DruckwaagenkanalPressure compensator channel
- 9494
- EntsperrkanalUnlocking channel
- 9696
- EntsperrkanalUnlocking channel
- 9898
- VentilscheibeValve disc
- 100100
- NotablassventilEmergency drain valve
- 102102
- VerbindungskanalConnecting channel
- 104104
- KugelBullet
- 106106
- MadenschraubeGrub screw
- 108108
- Kolbenpiston
- 110110
- DruckfederCompression spring
- 112112
- ProportionalmagnetProportional magnet
- 114114
- SchließkegelClosing cone
- 116116
- ModulkolbenModule piston
- 118118
- SchließfederClosing spring
- 120120
- VorsteuerventilkörperPilot valve body
- 122122
- AufstosskolbenImpact piston
- 124124
- DrucksensorPressure sensor
- 126126
- DrucksensorPressure sensor
- 128128
- WegaufnehmerDisplacement transducer
- 130130
- DrucksensorPressure sensor
- 132132
- DrucksensorPressure sensor
- 134134
- DrucksensorPressure sensor
- 136136
- SteuerraumControl room
- 138138
- SteuerraumControl room
- 140140
- SchaltventilSwitching valve
Claims (10)
- A lifting gear valve arrangement (14) for controlling a double-action lifting gear (2, 4) or an add-on unit, in particular of an agricultural commercial vehicle, comprising a continuously adjustable directional control valve (44) forming a metering aperture to which an individual pressure compensator (42) is assigned, via which a pressure medium volume flow flows to a working connection (A, B), wherein pressure medium flowing back via another working connection (A, B) flows off to a low pressure or tank connection (T) via the directional control valve (44), and a pressure limiting valve (56) positioned in a working channel (48, 50) between the directional control valve (44) and the working connection (A, B), characterized in that said pressure limiting valve (56) is designed to be proportionally adjustable, so that the pressure in said working channel (48, 50) may be limited to different maximum values as a function of different operating states, said directional control valve (44) being adapted to be adjusted by a control device (16) to a neutral position (0) or a floating position (c) on response of said pressure limiting valve (56), wherein the maximum pressure is differently adjustable as a function of different setpoint devices/operating devices (18, 20, 24).
- The lifting gear valve arrangement according to claim 1, wherein said pressure limiting valve (56) is designed such that it may be arranged on the working channel (50) that is connected to a pressure chamber (60) of said lifting gear (2, 4) or of said add-on unit which acts in the direction of "lowering."
- The lifting gear valve arrangement according to claim 1 or 2, wherein said pressure limiting valve (56) is adjustable to values between 0 and 250 bar.
- The lifting gear valve arrangement according to any of the preceding claims, wherein a secondary pressure limiting valve (58) is arranged in said other working channel (48).
- The lifting gear valve arrangement according to any of the preceding claims, wherein one lowering module (52, 54) each is arranged in said working channels (48, 50) for leakage oil-free blocking of the pressure medium.
- The lifting gear valve arrangement according to claim 5, wherein said lowering module (52, 54) is designed as a drain pressure compensation that is adjustable to a flowthrough position by a control pressure.
- The lifting gear valve arrangement according to any of the preceding claims, wherein said individual pressure compensator (42) is connected upstream of said directional control valve (44) and is impacted in the opening direction by the highest load pressure (LS) and the force of a pressure compensator spring (70), and in the closing direction by the pressure upstream of said directional control valve (44).
- The lifting gear valve arrangement according to any of the preceding claims, comprising a hand-operated emergency drain (100) via which a connection of the pressurized working channel (48, 50) to the tank (T) can be opened.
- The lifting gear valve arrangement according to any of the preceding claims, which is designed so as to be usable for controlling a rear lifting gear (2) or a front lifting gear (4) of a tractor (1).
- The lifting gear valve arrangement according to any of the preceding claims, comprising a switch valve (140) connected upstream of said pressure limiting valve (56).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102004033315A DE102004033315A1 (en) | 2004-07-09 | 2004-07-09 | lifting gear |
PCT/EP2005/007308 WO2006005496A1 (en) | 2004-07-09 | 2005-07-06 | Lifting gear valve arrangement |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1766146A1 EP1766146A1 (en) | 2007-03-28 |
EP1766146B1 EP1766146B1 (en) | 2011-09-14 |
EP1766146B2 true EP1766146B2 (en) | 2020-03-25 |
Family
ID=35207388
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05772453.6A Active EP1766146B2 (en) | 2004-07-09 | 2005-07-06 | Lifting gear valve arrangement |
Country Status (5)
Country | Link |
---|---|
US (1) | US8020485B2 (en) |
EP (1) | EP1766146B2 (en) |
AT (1) | ATE524617T1 (en) |
DE (1) | DE102004033315A1 (en) |
WO (1) | WO2006005496A1 (en) |
Families Citing this family (29)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102005005314A1 (en) | 2004-12-20 | 2006-06-22 | Bosch Rexroth Aktiengesellschaft | Valve arrangement and method for controlling a double-acting consumer |
DE102006004423B4 (en) | 2006-01-31 | 2018-08-02 | Robert Bosch Gmbh | Valve arrangement for controlling a hoist or attachment and method for controlling this |
DE102007040345A1 (en) | 2007-07-18 | 2009-01-22 | Robert Bosch Gmbh | Method for controlling a hoist and hoist |
DE102007040344A1 (en) | 2007-07-19 | 2009-01-22 | Robert Bosch Gmbh | Hoist and method for controlling such a hoist |
DE102008006879A1 (en) * | 2008-01-31 | 2009-08-06 | Hydac Filtertechnik Gmbh | Hydraulic valve device |
DE102009027453A1 (en) | 2009-07-03 | 2011-01-27 | Deere & Company, Moline | Agricultural vehicle |
DE102009042120B4 (en) * | 2009-09-18 | 2016-11-17 | Marco Systemanalyse Und Entwicklung Gmbh | valve assembly |
DE102010051690A1 (en) | 2010-11-17 | 2012-05-24 | Hydac Filtertechnik Gmbh | Hydraulic valve device |
EP2466152B1 (en) | 2010-12-17 | 2013-03-20 | HAWE Hydraulik SE | Electrohydraulic control device |
DE102011013771A1 (en) * | 2011-03-12 | 2012-09-13 | Robert Bosch Gmbh | Auxiliary drive for tools |
DE102011101553A1 (en) * | 2011-05-14 | 2012-11-15 | Robert Bosch Gmbh | hoist |
JP6338428B2 (en) * | 2014-04-11 | 2018-06-06 | Kyb株式会社 | Valve structure |
EP3020874B1 (en) * | 2014-11-12 | 2022-07-06 | John Deere Forestry Oy | A hydraulic control system for controlling a moveable device |
DE102015209657A1 (en) * | 2014-12-08 | 2016-06-23 | Robert Bosch Gmbh | Hydraulic valve assembly, hydraulic valve block with such a valve assembly, and hydraulic drive with it |
US10349571B2 (en) * | 2015-04-30 | 2019-07-16 | Kuhn Krause, Inc. | Constant pressure hydraulic circuit with relief protection independent of pressure circuit |
CN105035979B (en) * | 2015-08-05 | 2017-05-03 | 常德中联重科液压有限公司 | Balance valve group and hydraulic system |
US10590962B2 (en) | 2016-05-16 | 2020-03-17 | Parker-Hannifin Corporation | Directional control valve |
US9968033B2 (en) * | 2016-06-21 | 2018-05-15 | Macdon Industries Ltd. | Crop machine with an electronically controlled hydraulic cylinder flotation system |
US10617059B2 (en) * | 2016-06-21 | 2020-04-14 | Macdon Industries Ltd. | Crop machine with an electronically controlled hydraulic cylinder flotation system |
US10624263B2 (en) * | 2016-06-21 | 2020-04-21 | Macdon Industries Ltd | Crop machine with an electronically controlled hydraulic cylinder flotation system |
IT201700056889U1 (en) * | 2017-05-25 | 2018-11-25 | Faster Spa | CONNECTION FOR HYDRAULIC APPLICATIONS EQUIPPED WITH AT LEAST ONE DETECTION SENSOR |
DE102017115537A1 (en) | 2017-07-11 | 2019-01-17 | Liebherr-Hydraulikbagger Gmbh | Construction machinery |
DE102018004769A1 (en) * | 2018-06-13 | 2019-12-19 | Hydac Mobilhydraulik Gmbh | control device |
SE544628C2 (en) * | 2018-07-23 | 2022-09-27 | Joab Foersaeljnings Ab | Hydraulic system and method for controlling the speed and pressure of a hydraulic cylinder |
US10641297B2 (en) * | 2018-08-17 | 2020-05-05 | Robert Bosch Gmbh | Hydraulic control valve |
CN109853660B (en) * | 2018-12-29 | 2021-05-07 | 山东欧泰隆重工有限公司 | Intelligent control system of loader |
DE102020109975A1 (en) | 2020-04-09 | 2021-10-28 | Amazonen-Werke H. Dreyer SE & Co. KG | Agricultural work machine and method for operating an agricultural work machine |
DE102020208922B3 (en) | 2020-07-16 | 2021-12-09 | Robert Bosch Gesellschaft mit beschränkter Haftung | Valve arrangement |
DE102021203713A1 (en) * | 2021-04-15 | 2022-10-20 | Thomas Löcher | Method of hydraulically lowering tools onto a surface of an object |
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US4898078A (en) * | 1987-09-11 | 1990-02-06 | Deere & Company | Hydraulic system for a work vehicle |
US5186000A (en) | 1988-05-10 | 1993-02-16 | Hitachi Construction Machinery Co., Ltd. | Hydraulic drive system for construction machines |
IN170798B (en) | 1988-05-12 | 1992-05-23 | Hitachi Construction Machinery | |
EP0438604B1 (en) | 1989-08-16 | 1997-02-05 | Kabushiki Kaisha Komatsu Seisakusho | Hydraulic circuit device |
DE4135013C2 (en) | 1991-10-23 | 2000-07-27 | Linde Ag | Hydraulic drive system |
DE4137963C2 (en) * | 1991-10-30 | 1995-03-23 | Rexroth Mannesmann Gmbh | Valve arrangement for load-independent control of several hydraulic consumers |
JP3528981B2 (en) * | 1994-08-30 | 2004-05-24 | 株式会社小松製作所 | Hydraulic circuit for boom cylinder of hydraulic excavator |
DE4433633C1 (en) | 1994-09-21 | 1995-12-07 | Wessel Hydraulik | Hydraulic switching unit for operation of exchangeable additional device on hydraulic excavators |
DE19939967C2 (en) | 1999-01-09 | 2003-10-23 | Walterscheid Gmbh Gkn | Hoist for lower links of an attachment device of a tractor |
DK1069317T3 (en) | 1999-07-10 | 2003-12-08 | Bosch Rexroth Ag | Directional control valve plate, especially for a mobile work machine |
DE10006908A1 (en) * | 2000-02-16 | 2001-08-23 | Caterpillar Sarl Genf Geneva | Hydraulic cylinder unit for raising and lowering front arm on root harvester has branch pipe leading back to oil tank which is fitted with shut-off valve and pressure-regulating valve |
DE10219717B3 (en) * | 2002-05-02 | 2004-02-05 | Sauer-Danfoss (Nordborg) A/S | Hydraulic valve arrangement |
-
2004
- 2004-07-09 DE DE102004033315A patent/DE102004033315A1/en not_active Withdrawn
-
2005
- 2005-07-06 EP EP05772453.6A patent/EP1766146B2/en active Active
- 2005-07-06 AT AT05772453T patent/ATE524617T1/en active
- 2005-07-06 WO PCT/EP2005/007308 patent/WO2006005496A1/en active Application Filing
- 2005-07-06 US US11/571,730 patent/US8020485B2/en active Active
Non-Patent Citations (1)
Title |
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BOSCH REXROTH AG: "LUDV Steuerblock in Mono-/Scheibenbauweise Type M7-22", BOSCH REXROTH RD 64 295, 7 February 2003 (2003-02-07), pages 1 - 16 † |
Also Published As
Publication number | Publication date |
---|---|
EP1766146B1 (en) | 2011-09-14 |
ATE524617T1 (en) | 2011-09-15 |
US20070277519A1 (en) | 2007-12-06 |
DE102004033315A1 (en) | 2006-02-09 |
WO2006005496A1 (en) | 2006-01-19 |
EP1766146A1 (en) | 2007-03-28 |
US8020485B2 (en) | 2011-09-20 |
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