EP2157320A1 - Hydraulic device for a hydro motor - Google Patents

Hydraulic device for a hydro motor Download PDF

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Publication number
EP2157320A1
EP2157320A1 EP08014795A EP08014795A EP2157320A1 EP 2157320 A1 EP2157320 A1 EP 2157320A1 EP 08014795 A EP08014795 A EP 08014795A EP 08014795 A EP08014795 A EP 08014795A EP 2157320 A1 EP2157320 A1 EP 2157320A1
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EP
European Patent Office
Prior art keywords
control
pressure
hydraulic
valve
hydraulic motor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP08014795A
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German (de)
French (fr)
Other versions
EP2157320B1 (en
Inventor
Martin Heusser
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Hawe Hydraulik SE
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Hawe Hydraulik SE
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Publication date
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Priority to DE200850002003 priority Critical patent/DE502008002003D1/en
Priority to EP20080014795 priority patent/EP2157320B1/en
Publication of EP2157320A1 publication Critical patent/EP2157320A1/en
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Publication of EP2157320B1 publication Critical patent/EP2157320B1/en
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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/321—Directional control characterised by the type of actuation mechanically
    • F15B2211/324—Directional control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/56—Control of an upstream pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/565—Control of a downstream pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/61—Secondary circuits
    • F15B2211/611—Diverting circuits, e.g. for cooling or filtering
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7107—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being mechanically linked

Definitions

  • the invention relates to a hydraulic control according to the preamble of patent claim 1.
  • Such hydraulic controls are u.a. used in agricultural vehicles, such as hydraulic plows, or in snow plows, deep hole drills, or the like, wherein the shut-off neutral position of the three-position spool control valve hydraulically blocks the hydraulic motor once it has been brought into or against a predetermined position against or under the load.
  • the shut-off neutral position of the three-position spool control valve hydraulically blocks the hydraulic motor once it has been brought into or against a predetermined position against or under the load.
  • no three-position slide control valve can be used with pronounceabsperrender neutral position, but so far additional hydraulic components are integrated into the hydraulic control, which make it possible to open a large cross-sectional Abströmweg to the reservoir, if necessary to at least one working fluid side of the Hydraulic motor to relieve.
  • This may be, for example, a second three-position spool control valve, or an external element, which, however, means additional and costly overhead.
  • Another possibility is to provide a four-position valve control valve, which also requires a lot of effort and especially as a control valve may have the disadvantage that the usable control strokes are shortened.
  • the invention has for its object to provide a hydraulic control of the type mentioned, which still allows the active discharge of at least one working fluid side of the hydraulic motor without costly additional hydraulic components with a three-position slide control valve with shut-off neutral position.
  • a fictitious fourth control position for the three-position slide control valve is realized so to speak by means of the working fluid Abströmweg equipped, so slightly compared to a usually provided without pressure scale or arranged for this purpose pressure balance on the pressure side to the hydraulic motor actively relieve (floating position).
  • This does not require additional expensive hydraulic components, although the hydraulic controller operates as if it contained a four position spool control valve.
  • the load pressure signal circuit is optionally relieved via at least one releasable in a control position of the three-position spool control valve control pressure Abströmweg in three-position valve control valve to the reservoir.
  • This control pressure Abströmweg can be realized with little structural effort in the three-position valve control valve, without noticeably shortening the control stroke of this control position in which this control pressure Abströmweg is released. Because it does not need a large cross section to be opened, but only a cross section, which is sufficient to relieve the control pressure of the load pressure signal circuit. The large cross-sectional outflow for the working fluid, however, is opened in the pressure compensator.
  • the load pressure signal circuit is optionally relieved via a arranged between the reservoir and the three-position control valve secondary pressure limiting the hydraulic motor to the reservoir.
  • the secondary pressure limitation is optionally without existing equipment of the hydraulic control and is modified for the additional task of depressurizing the hydraulic motor with a solenoid valve, suitably a proportional solenoid valve.
  • the load pressure signal circuit is relieved either via a arranged between the hydraulic motor and the reservoir or between the hydraulic motor and the three-position valve control valve relief device.
  • the additional expense for this relief device is low.
  • the working fluid Abströmweg in the pressure compensator not only an on / off but even a pressure reduction function can be generated except for a limited by a control spring of the pressure balance minimum pressure.
  • the equipped with the additional working fluid Abströmweg pressure compensator which frees this Abströmweg in the shut-off, thus fulfilling the discharge so to speak, the function of a regulating pressure reducing valve, and otherwise a proportional inlet regulator.
  • the pressure compensator basically operates as a function of the spring force of the control spring and the pressures as a normal supply regulator, but can also work as a proportional flow regulator by influencing the load pressure signal, for example, to set a lower pressure difference than in normal work.
  • At least one proportional solenoid valve preferably a proportional solenoid seat valve, is provided downstream of a throttle, and the load pressure signal for the pressure compensator is between Throttle and the proportional solenoid valve tapped.
  • the proportional solenoid valve can be used in conjunction with the throttle to make an exactly predeterminable relief of the pressure signal for the pressure compensator, and the pressure compensator is modulated in accordance finally brought to the full shut-off position.
  • the three-position slide control valve is expediently a pressure control valve with load pressure signal tap.
  • this control pressure Abströmweg located in a spool at the end or outside the control range of the spool in the control position in which the pressure relief of the hydraulic motor is effected. In this way, since only a very small cross section has to be released with a very small adjusting movement, the control stroke in this control position is not noticeably shortened.
  • the secondary pressure limitation is provided at least for the working fluid side of the hydraulic motor to be relieved in this way, or, suitably, secondary pressure limits are provided for both working fluid sides of the hydraulic motor.
  • this load pressure signal line is connected to at least one working fluid side of the hydraulic motor.
  • this load pressure signal line is connected via a shuttle valve load pressure independent automatically to each working fluid side of the hydraulic motor to tap for the pressure balance one or the respective higher load pressure.
  • the hydromotor As soon as the hydromotor is actively relieved of both working fluid sides to the reservoir, it can be adjusted under a load and / or by means of the further hydraulic motor, as if its three-position spool control valve also had a further non-blocking neutral position.
  • that working fluid side of the hydraulic motor is relieved via the pressure compensator, which is not already relieved to the reservoir in the corresponding control position of the three-position slide control valve.
  • a floating position of the hydraulic motor is adjusted, since both sides of the working fluid are equal or substantially equal to pressure.
  • This is particularly useful, for example, for a hydraulic motor which is designed as a differential cylinder and has different pressure application surfaces in the piston-side and piston rod-side chambers as well as fluid volumes of different size to be displaced.
  • the Fig. 1 and 2 illustrate embodiments of at least one three-position spool control valve 3, 3 'containing hydraulic controls S, such as are used in vehicles, especially in agricultural vehicles, road service vehicles or the like .
  • This hydraulic plows, snow plows, deep hole drills or similar devices with at least one load-moving hydraulic motor M, M 'in question, although the hydraulic control also has other applications, especially if a hydraulic motor M must be both hydraulically blocked and hydraulically relieved.
  • the hydraulic motor M for example, a differential cylinder, a load L, which acts here in the retraction of the differential cylinder.
  • the load L may be, for example, a snow plow, an hydraulic plow or a deep hole drill.
  • Both working fluid sides of the hydraulic motor M are connected via working lines 1, 2 to corresponding ports of the three position spool control valve 3, in the embodiment shown, a three position pressure regulating spool control valve 3 (indicated by the two parallel lines above and below the symbol block).
  • the three-position spool control valve 3 is connected to a pressure port 10 via a pressure line 5 to a pump P (with check valve) and a three-way pressure compensator 4, and parallel to a reservoir R.
  • the three-way pressure compensator 4 includes a Häströmungsweg 7, the between Ports 12 and 9 is adjustable, and a Häfluid-Abströmweg 11, which is adjustable between the terminal 9 and a terminal 8. Intermediate positions are, as usual with a pressure compensator, also adjustable.
  • Fig. 1 the pressure compensator 4 is shown in the open position, in which the working fluid flow path 7 connects the ports 12 and 9, whereas the working fluid Abströmweg 11 is shut off.
  • the pressure compensator 4 plays between the position shown and a shut-off position in which the pressure line 5 is shut off at the connection 12, whereas the working fluid outflow path 11 connects the connections 9 and 8 to a return line 6 and the reservoir R.
  • the pressure compensator 4 is in the direction of adjustment to the in Fig. 1 shown position by a control spring 16 and acted upon at a control pressure port 25 with a load pressure signal which is tapped at a node 22 of a load pressure signal line 17.
  • the pressure compensator 4 is acted upon at a control pressure connection 15 by control pressure tapped between the pressure compensator 4 and the pressure connection 10 from a control line 13 and via a throttle 14.
  • the load pressure signal line 17 is connected to a shuttle valve 20 which is arranged between load pressure taps 18, 19, for example, the working lines 1, 2.
  • the load pressure signal line 17 could be e.g. only be connected to the tap 18, and the shuttle valve 20 are omitted.
  • a throttle 21 is provided upstream of the node 22.
  • a branch 17 'of the load pressure signal line leads to reservoir R.
  • a proportional solenoid valve 23 which, for example, is normally kept open by a control spring and pressure in a pilot line and when proportional solenoid 24 is energized is brought to a corresponding proportional shut-off or throttle position.
  • the three-position spool control valve 3 has a neutral position 0 (as shown) in which the hydraulic motor M is hydraulically locked.
  • the three-position spool control valve 3 is movable from the neutral position 0 in, e.g. druckregelnde, control positions a, b adjust, wherein in the control position b from the pressure port 10, the working line 2 and the working line 1 are relieved to the reservoir R, whereas in the control position a of the pressure port 10 connected to the working line 1 and the working line 2 to the reservoir R are relieved.
  • a fourth control position of the three-position valve control valve 3 is realized, in which in the respective control position a, b via the one working fluid flow path W, the working fluid side of the hydraulic motor M is actively relieved to the reservoir R, which is not already relieved via the three-position slide control valve 3 to the reservoir R.
  • the pressure compensator 4 is adjusted to its shut-off position, even with the pump P running, in which the load pressure signal at the control pressure port 25 is relieved via the proportional solenoid valve 23 to the reservoir R.
  • the throttle 21 generates a pressure gradient, so that the branch 17 'can be proportionally relieved and also the hydraulic motor M is relieved to the pressurized working fluid side in a selectable extent.
  • the pressure compensator 4 makes in this case a finely adjustable pressure reducing function, since it allows the pressure at the pressurized working fluid side of the hydraulic motor M übe the then maximum open working fluid flow path W infinitely reduced practically to zero (practically up to a pressure value of a few Bar, according to the force of the control spring 16 of the pressure compensator 4).
  • the pressure compensator 4 operates according to the pressures at the terminals 25, 15 in the manner of an inlet regulator, which relieves the pressure port 10 to the reservoir R in the neutral position 0.
  • the three-position spool control valve 3 (control valve) has the load pressure signal taps 18, 19, wherein a spool 35 in the control position a can assume a further fictitious control position a1 in which a control pressure outflow path 30 to the reservoir R (via a control line 32) is releasable, and, for example, the working line 1 is relieved of the then open to maximum size working fluid flow path W and the pressure compensator 4. Since the control pressure Abströmweg 30 requires only very small cross-section and at the end of the control stroke at maximum size of the working fluid flow path W is open to reduce only the control pressure of the load pressure signal circuit, the control stroke of the control position a is not noticeably reduced by this additional function.
  • the Abströmweg 30 could alternatively be opened by a small adjusting stroke of the spool 35 outside the control stroke.
  • the load pressure taps 18, 19 in the working lines 1, 2 are each connected via control pressure channels 26, 27 in the respective control positions a, b with a load pressure signal circuit 28 which leads via the throttle 21 to the control pressure port 25 of the pressure compensator 4.
  • the load pressure signal circuit 28 is relieved via a control pressure channel 29 in the three-position slide control valve 3 and the control line 32 to the reservoir R.
  • the three-position slide control valve 3 is brought into the additional control position a1, in which the load pressure signal via the control channel 30 for Reservoir R is relieved.
  • the control pressure port 25 of the pressure compensator 4 With the disappearance of the control pressure at the control pressure port 25 of the pressure compensator 4, this is brought into its shut-off position in which the Schwarzfluid-Abströmweg 11 is opened to the reservoir R and the working line 1 is relieved via the Schwarzfluid-Abströmweg 11 with a large cross-section.
  • the working line 2 is in the control position a1 anyway connected to the reservoir R.
  • the hydraulic motor M is brought in this way in a floating position.
  • the hydraulic control S in Fig. 2 a further, via working lines 1 ', 2' operable hydraulic motor M 'and a parallel connected further three-position slide control valve 3 '(with shut-off neutral position 0' and secondary pressure limitations B1 ', B2').
  • the further hydraulic motor M ' is for example coupled to the hydraulic motor M or coupled to the hydraulic motor M at unloaded working lines 1, 2 (eg in the control position a1 of the three-position control valve 3, ie in a floating position) to adjust.
  • FIG Fig. 2 are as a further option in addition to the three-position slide control valve 3 secondary pressure B1, B2 (or at least the secondary pressure limitation B1 for the working line 1) provided in the load pressure signal circuit 28 whose purpose is in principle, the maximum pressures in the working lines 1, 2 via the pressure compensator 4 Flow regulator) (possibly to different pressure values). Since the secondary pressure limitations B1 and B2 are constructed identically, only the secondary pressure limitation B1 is explained.
  • the secondary pressure limitation B1 is connected in the control position a of the spool 35 via a short-circuit channel 36 with the load pressure signal circuit 28 and includes a pilot-operated pressure relief valve 33 which opens pressure-dependent to the reservoir R.
  • a proportional solenoid seat valve 34 is provided, wherein the load pressure signal is present not only at the control pressure port 25 of the pressure compensator 4 but also on the pressure relief valve 33 and the proportional solenoid seat valve 34.
  • the pilot-operated pressure limiting valve 33 limits a maximum height of the load pressure signal.
  • the proportional solenoid seat valve 34 is due to pilot control, and optionally also by a spring in the passage position shown can be brought and is adjusted proportionally by the proportional solenoid 24 in a shut-off position.
  • the proportional solenoid seat valve 34 is, for example, basically provided to achieve a safety function in the secondary pressure limitation B1, for example, to completely reduce the load pressure signal as needed and bring the pressure compensator 4 in the shut-off, so that the hydraulic motor M no longer against the load L. is moving.
  • the proportional solenoid seat valve 34 is here used in combination with the pressure compensator 4 to selectively relieve the working line 1 of the hydraulic motor M.
  • the proportional solenoid 24 is first de-energized at, for example, in the control position a verticianm three-position slide control valve 3, so that the load pressure signal is reduced and the pressure compensator 4 assumes its shut-off position.
  • the working line 1 becomes active via the working fluid outflow path 11 in the pressure compensator 4 and the working line 2 in each case in each case connected to the reservoir R, so that the hydraulic motor M enters a floating position.
  • the proportional solenoid 24 makes it possible to accurately control the degree of reduction of the load pressure signal, eg with a mild ramp function or only up to a certain pressure value.
  • both relief possibilities of Fig. 2 be provided and used, or only one (ie either the control position a1 and one or two secondary pressure limitations B1, B2 with the seat valves 34, 34 ', or only the control position a1 or only one or both secondary pressure limitations B1, B2.
  • another control position b1 (not shown) for the control position b could be analogously explained as for the control position a1, with the working fluid flow path W being provided in maximum size.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The control (S) has a three-way pressure maintenance valve (4) arranged between a pump (P) and a pressure connector (10) of a three position-slide control valve (3) i.e. pressure regulating-control valve. The maintenance valve is designed with a working fluid-discharge path (11) to a reservoir (R). The path connects the connector with the reservoir, in a blocking position of the maintenance valve. A load pressure signal circuit of the control valve is alternatively released at the reservoir for desired releasing of a hydro-motor (M) via the path in the maintenance valve. The pressure maintenance valve is operated as a proportional feed control unit via an active releasing of the load pressure signals.

Description

Die Erfindung betrifft eine Hydrauliksteuerung gemäß Oberbegriff des Patentanspruchs 1.The invention relates to a hydraulic control according to the preamble of patent claim 1.

Derartige Hydrauliksteuerungen werden u.a. in landwirtschaftlichen Fahrzeugen, wie Hydraulikpflügen, oder in Schneepflügen, Tieflochbohrem, oder dgl. verwendet, wobei die absperrende Neutralstellung des Dreistellungs-Schiebersteuerventils den Hydromotor hydraulisch blockiert, sobald er gegen die oder unter der Last in eine bestimmte Position gebracht wurde. Nun gibt es für solche Hydrauliksteuerungen, insbesondere in den obenerwähnten Fahrzeugen, auch das Erfordernis, die hydraulische Blockierung, gegebenenfalls ohne Verstellung des Hydromotors aufzuheben, und zwar bei im Betrieb befindlicher Pumpe, oder sogar eine Schwimmstellung einzustellen, in der sich der Hydromotor ohne Pumpendruck verstellen lässt. Da auch die hydraulische Blockierung erforderlich ist, lässt sich kein Dreistellungs-Schiebersteuerventil mit nichtabsperrender Neutralstellung benutzen, sondern es werden bisher zusätzliche hydraulische Komponenten in die Hydrauliksteuerung integriert, die es ermöglichen, bei Bedarf einen großquerschnittigen Abströmweg zum Reservoir zu öffnen, um zumindest eine Arbeitsfluidseite des Hydromotors zu entlasten. Dies kann beispielsweise ein zweites Dreistellungs-Schiebersteuerventil sein, oder ein externes Element, was jedoch zusätzlichen und kostenintensiven Mehraufwand bedeutet. Eine weitere Möglichkeit besteht darin, ein Vierstellungs-Schiebersteuerventil vorzusehen, das ebenfalls hohen Aufwand bedingt und speziell als Regelventil den Nachteil haben kann, dass die nutzbaren Regelhübe verkürzt sind.Such hydraulic controls are u.a. used in agricultural vehicles, such as hydraulic plows, or in snow plows, deep hole drills, or the like, wherein the shut-off neutral position of the three-position spool control valve hydraulically blocks the hydraulic motor once it has been brought into or against a predetermined position against or under the load. Now there is for such hydraulic controls, especially in the above-mentioned vehicles, the requirement to suspend the hydraulic lock, possibly without adjustment of the hydraulic motor, in fact when operating pump, or even adjust a floating position in which adjust the hydraulic motor without pump pressure leaves. Since the hydraulic blocking is required, no three-position slide control valve can be used with nichtabsperrender neutral position, but so far additional hydraulic components are integrated into the hydraulic control, which make it possible to open a large cross-sectional Abströmweg to the reservoir, if necessary to at least one working fluid side of the Hydraulic motor to relieve. This may be, for example, a second three-position spool control valve, or an external element, which, however, means additional and costly overhead. Another possibility is to provide a four-position valve control valve, which also requires a lot of effort and especially as a control valve may have the disadvantage that the usable control strokes are shortened.

Der Erfindung liegt die Aufgabe zugrunde, eine Hydrauliksteuerung der eingangs genannten Art anzugeben, die ohne kostenintensive Zusatz-Hydraulikkomponenten mit einem Dreistellungs-Schiebersteuerventil mit absperrender Neutralstellung dennoch die aktive Entlastung zumindest einer Arbeitsfluidseite des Hydromotors erlaubt.The invention has for its object to provide a hydraulic control of the type mentioned, which still allows the active discharge of at least one working fluid side of the hydraulic motor without costly additional hydraulic components with a three-position slide control valve with shut-off neutral position.

Die gestellte Aufgabe wird mit den Merkmalen des Patentanspruchs 1 gelöst.The stated object is achieved with the features of claim 1.

Erfindungsgemäß wird mittels der mit dem Arbeitsfluid-Abströmweg ausgestatteten, also geringfügig gegenüber einer meist ohnedies vorgesehenen Druckwaage modifizierten oder einer für diesen Zweck eingeordneten Druckwaage auf der Druckseite sozusagen eine fiktive vierte Steuerstellung für das Dreistellungs-Schiebersteuerventil realisiert, um den Hydromotor aktiv entlasten zu können (Schwimmstellung). Dazu werden keine zusätzlichen kostenintensiven Hydraulikkomponenten benötigt, obwohl die Hydrauliksteuerung so arbeitet, als enthielte sie ein Vierstellungs-Schiebersteuerventil. Sobald die Druckwaage durch aktive Entlastung des Lastdrucksignalkreises zur Absperrstellung gebracht wird, ist der Arbeitsfluid-Abströmweg zum Reservoir freigegeben, und kann zumindest eine Arbeitsfluidseite des Hydromotors in einer Steuerstellung des Dreistellungs-Schiebersteuerventils außerhalb der Neutralstellung gewollt und aktiv entlastet werden.According to the invention, a fictitious fourth control position for the three-position slide control valve is realized so to speak by means of the working fluid Abströmweg equipped, so slightly compared to a usually provided without pressure scale or arranged for this purpose pressure balance on the pressure side to the hydraulic motor actively relieve (floating position). This does not require additional expensive hydraulic components, although the hydraulic controller operates as if it contained a four position spool control valve. Once the pressure compensator is brought to the shut-off position by actively relieving the load pressure signal circuit, the working fluid outflow path to the reservoir is released, and at least one working fluid side of the hydraulic motor in a control position of the three-position spool control valve can be intentionally and actively relieved off the neutral position.

Für diese mit meist ohnedies vorhandenen Komponenten der Hydrauliksteuerung, die nur geringfügig und kostengünstig modifiziert wird, geschaffene Entlastungsmöglichkeit gibt es mehrere Varianten.There are several variants for this, usually without already existing components of the hydraulic control, which is modified only slightly and inexpensively, relief option.

Bei einer zweckmäßigen Ausführungsform wird der Lastdrucksignalkreis wahlweise über wenigstens einen in einer Steuerstellung des Dreistellungs-Schiebersteuerventils freigebbaren Steuerdruck-Abströmweg im Dreistellungs-Schiebersteuerventil zum Reservoir entlastet. Dieser Steuerdruck-Abströmweg lässt sich mit geringem baulichen Aufwand im Dreistellungs-Schiebersteuerventil realisieren, ohne den Regelhub dieser Steuerstellung spürbar zu verkürzen, in der dieser Steuerdruck-Abströmweg freigegeben wird. Denn es braucht kein großer Querschnitt geöffnet zu werden, sondern nur ein Querschnitt, der zur Entlastung des Steuerdrucks des Lastdruck-Signalkreises ausreicht. Der großquerschnittige Abströmweg für das Arbeitsfluid wird hingegen in der Druckwaage geöffnet.In an expedient embodiment, the load pressure signal circuit is optionally relieved via at least one releasable in a control position of the three-position spool control valve control pressure Abströmweg in three-position valve control valve to the reservoir. This control pressure Abströmweg can be realized with little structural effort in the three-position valve control valve, without noticeably shortening the control stroke of this control position in which this control pressure Abströmweg is released. Because it does not need a large cross section to be opened, but only a cross section, which is sufficient to relieve the control pressure of the load pressure signal circuit. The large cross-sectional outflow for the working fluid, however, is opened in the pressure compensator.

Bei einer anderen zweckmäßigen Ausführungsform wird der Lastdruck-Signalkreis wahlweise über eine zwischen dem Reservoir und dem Dreistellungs-Steuerventil angeordnete Sekundärdruckbegrenzung des Hydromotors zum Reservoir entlastet. Die Sekundärdruckbegrenzung ist gegebenenfalls ohnedies existente Ausstattung der Hydrauliksteuerung und wird für die zusätzliche Aufgabe der Druckentlastung des Hydromotors mit einem Magnetventil, zweckmäßig einem Proportionalmagnetventil, modifiziert.In another expedient embodiment, the load pressure signal circuit is optionally relieved via a arranged between the reservoir and the three-position control valve secondary pressure limiting the hydraulic motor to the reservoir. The secondary pressure limitation is optionally without existing equipment of the hydraulic control and is modified for the additional task of depressurizing the hydraulic motor with a solenoid valve, suitably a proportional solenoid valve.

Bei einer weiteren, zweckmäßigen Ausführungsform wird der Lastdrucksignalkreis wahlweise über eine zwischen dem Hydromotor und dem Reservoir bzw. zwischen dem Hydromotor und dem Dreistellungs-Schiebersteuerventil angeordnete Entlastungsvorrichtung entlastet. Der zusätzliche Aufwand für diese Entlastungsvorrichtung ist gering. Gegebenenfalls ist diese Entlastungsvorrichtung oder ist eine Hauptkomponente dieser Entlastungsvorrichtung, z.B. zum Bereitstellen einer Schock- oder Sicherheitsfunktion, ohnedies vorhanden.In a further expedient embodiment of the load pressure signal circuit is relieved either via a arranged between the hydraulic motor and the reservoir or between the hydraulic motor and the three-position valve control valve relief device. The additional expense for this relief device is low. Optionally, this unloading device or is a major component of this unloading device, eg for providing a shock or safety function, is present anyway.

Besonders zweckmäßig ist mit dem Arbeitsfluid-Abströmweg in der Druckwaage nicht nur eine Auf/Zu- sondern sogar eine Druckminderungs-Funktion bis auf einen von einer Regelfeder der Druckwaage begrenzten Minimaldruck erzeugbar. Dies bedeutet, dass die Druckentlastung der zumindest einen Arbeitsfluidseite des Hydromotors sehr feinfühlig bis auf einen jeweils zweckmäßigen Wert ausführbar ist. Die mit dem zusätzlichen Arbeitsfluid-Abströmweg ausgestattete Druckwaage, die diesen Abströmweg in der Absperrstellung freimacht, erfüllt somit bei der Entlastung sozusagen die Funktion eines regelnden Druckminderventils, und sonst eines proportionalen Zulaufreglers. Damit ist gemeint, dass die Druckwaage grundsätzlich in Abhängigkeit von der Federkraft der Regelfeder und den Drücken als normaler Zulaufregler arbeitet, jedoch durch eine Beeinflussung des Lastdrucksignals alternativ auch als proportionaler Zulaufregler arbeiten kann, beispielsweise um eine geringere Druckdifferenz einzustellen als beim normalen Arbeiten.Particularly useful is the working fluid Abströmweg in the pressure compensator not only an on / off but even a pressure reduction function can be generated except for a limited by a control spring of the pressure balance minimum pressure. This means that the pressure relief of the at least one working fluid side of the hydraulic motor is very sensitively executable except for a respective appropriate value. The equipped with the additional working fluid Abströmweg pressure compensator, which frees this Abströmweg in the shut-off, thus fulfilling the discharge so to speak, the function of a regulating pressure reducing valve, and otherwise a proportional inlet regulator. This means that the pressure compensator basically operates as a function of the spring force of the control spring and the pressures as a normal supply regulator, but can also work as a proportional flow regulator by influencing the load pressure signal, for example, to set a lower pressure difference than in normal work.

Bei der Ausführungsform, bei der die Sekundärdruckbegrenzung oder die Entlastungsvorrichtung für die Druckentlastung der zumindest einen Arbeitsfluidseite des Hydromotors verwendet wird, ist wenigstens ein Proportionalmagnet-Ventil, vorzugsweise ein Proportionalmagnet-Sitzventil, stromab einer Drossel vorgesehen, und wird das Lastdrucksignal für die Druckwaage zwischen der Drossel und dem Proportionalmagnet-Ventil abgegriffen. Über das Proportionalmagnet-Ventil lässt sich im Zusammenspiel mit der Drossel eine exakt vorherbestimmbare Entlastung des Drucksignals für die Druckwaage vornehmen, und wird die Druckwaage entsprechend moduliert schließlich bis in die volle Absperrstellung gebracht.In the embodiment in which the secondary pressure relief or discharge device is used for pressure relief of the at least one working fluid side of the hydraulic motor, at least one proportional solenoid valve, preferably a proportional solenoid seat valve, is provided downstream of a throttle, and the load pressure signal for the pressure compensator is between Throttle and the proportional solenoid valve tapped. The proportional solenoid valve can be used in conjunction with the throttle to make an exactly predeterminable relief of the pressure signal for the pressure compensator, and the pressure compensator is modulated in accordance finally brought to the full shut-off position.

Um eine lastunabhängige Regelung des Hydromotors zu erzielen, ist das Dreistellungs-Schiebersteuerventil zweckmäßig ein Druckregel-Steuerventil mit Lastdrucksignal-Abgriff. In der Ausführungsform, in der der Steuerdruck-Abströmweg zum Reservoir im Dreistellungs-Schiebersteuerventil geöffnet werden kann, befindet sich dieser Steuerdruck-Abströmweg in einem Kolbenschieber am Ende oder außerhalb des Regelbereiches des Kolbenschiebers in der Steuerstellung, in der die Druckentlastung des Hydromotors bewirkt wird. Auf diese Weise wird, da mit einer sehr kleinen Stellbewegung nur ein sehr kleiner Querschnitt freigegeben werden muss, der Regelhub in dieser Steuerstellung nicht spürbar verkürzt.In order to achieve a load-independent control of the hydraulic motor, the three-position slide control valve is expediently a pressure control valve with load pressure signal tap. In the embodiment in which the control pressure outflow path to the reservoir in the three-position spool control valve can be opened, this control pressure Abströmweg located in a spool at the end or outside the control range of the spool in the control position in which the pressure relief of the hydraulic motor is effected. In this way, since only a very small cross section has to be released with a very small adjusting movement, the control stroke in this control position is not noticeably shortened.

In der Ausführungsform, in der die Sekundärdruckbegrenzung zum Entlasten des Lastdrucksignals eingesetzt wird, ist die Sekundärdruckbegrenzung zumindest für die auf diese Weise zu entlastende Arbeitsfluidseite des Hydromotors vorgesehen, oder sind, zweckmäßig, Sekundärdruckbegrenzungen für beide Arbeitsfluidseiten des Hydromotors vorgesehen.In the embodiment in which the secondary pressure limitation is used for relieving the load pressure signal, the secondary pressure limitation is provided at least for the working fluid side of the hydraulic motor to be relieved in this way, or, suitably, secondary pressure limits are provided for both working fluid sides of the hydraulic motor.

Dies ermöglicht es, den Sekundärdruck für beide Arbeitsfluidseiten des Hydromotors unterschiedlich einzustellen, und wahlweise, d.h. bei Bedarf, zusätzlich zumindest eine Arbeitsfluidseite zu entlasten.This makes it possible to set the secondary pressure differently for both working fluid sides of the hydraulic motor, and optionally, i. if necessary, in addition to relieve at least one working fluid side.

Bei der Ausführungsform mit der getrennt angeordneten Entlastungsvorrichtung kann diese in einer Lastdrucksignalleitung platziert sein, die an zumindest eine Arbeitsfluidseite des Hydromotors angeschlossen ist. Vorzugsweise, ist diese Lastdrucksignalleitung sogar über ein Wechselventil lastdruckabhängig selbsttätig an jede Arbeitsfluidseite des Hydromotors anschließbar, um für die Druckwaage einen bzw. den jeweils höheren Lastdruck abzugreifen.In the embodiment with the separately disposed relief device, it may be placed in a load pressure signal line connected to at least one working fluid side of the hydraulic motor. Preferably, this load pressure signal line is connected via a shuttle valve load pressure independent automatically to each working fluid side of the hydraulic motor to tap for the pressure balance one or the respective higher load pressure.

Sobald der Hydromotor aktiv an beiden Arbeitsfluidseiten zum Reservoir entlastet ist, lässt er sich unter einer Last oder/und mittels des weiteren Hydromotors verstellen, und zwar so, als ob sein Dreistellungs-Schiebersteuerventil auch eine weitere, nicht absperrende Neutralstellung hätte.As soon as the hydromotor is actively relieved of both working fluid sides to the reservoir, it can be adjusted under a load and / or by means of the further hydraulic motor, as if its three-position spool control valve also had a further non-blocking neutral position.

Zweckmäßig wird diejenige Arbeitsfluidseite des Hydromotors über die Druckwaage entlastet, die in der entsprechenden Steuerstellung des Dreistellungs-Schiebersteuerventils nicht ohnedies zum Reservoir entlastet ist. Auf diese Weise wird eine Schwimmstellung des Hydromotors eingestellt, da beide Arbeitsfluidseiten gleich oder im Wesentlichen gleich druckentlastet werden. Dies ist beispielsweise besonders zweckmäßig für einen Hydromotor, der als Differentialzylinder ausgebildet ist und unterschiedliche Druckbeaufschlagungsflächen in den kolbenseitigen und kolbenstangenseitigen Kammern sowie unterschiedlich große zu verdrängende Fluidvolumina hat.Suitably, that working fluid side of the hydraulic motor is relieved via the pressure compensator, which is not already relieved to the reservoir in the corresponding control position of the three-position slide control valve. In this way, a floating position of the hydraulic motor is adjusted, since both sides of the working fluid are equal or substantially equal to pressure. This is particularly useful, for example, for a hydraulic motor which is designed as a differential cylinder and has different pressure application surfaces in the piston-side and piston rod-side chambers as well as fluid volumes of different size to be displaced.

Anhand der Zeichnungen werden Ausführungsformen des Erfindungsgegenstandes erläutert. Es zeigen:

Fig. 1
ein Blockschaltbild einer ersten Ausführungsform einer Hydrauliksteuerung mit einer eigenständigen Entlastungsvorrichtung für einen Lastdrucksignalkreis, und
Fig. 2
ein Blockschaltbild einer weiteren Ausführungsform einer Hydrauliksteuerung mit zwei unterschiedlichen, gegebenenfalls kombiniert nutzbaren Lastdrucksignalkreis-Entlastungen.
With reference to the drawings, embodiments of the subject invention will be explained. Show it:
Fig. 1
a block diagram of a first embodiment of a hydraulic control with a stand-alone relief device for a load pressure signal circuit, and
Fig. 2
a block diagram of another embodiment of a hydraulic control with two different, optionally combined usable load pressure signal circuit reliefs.

Die Fig. 1 und 2 illustrieren Ausführungsformen von zumindest ein Dreistellungs-Schiebersteuerventil 3, 3' enthaltenden Hydrauliksteuerungen S, wie sie beispielsweise in Fahrzeugen verwendbar sind, insbesondere in landwirtschaftlichen Fahrzeugen, Straßendienstfahrzeugen oder dgl.. Speziell kommen hierfür Hydraulikpflüge, Schneepflüge, Tieflochbohrer oder ähnliche Geräte mit wenigstens einem lastbewegenden Hydromotor M, M' in Frage, obwohl die Hydrauliksteuerung auch andere Einsatzfälle hat, insbesondere, wenn ein Hydromotor M sowohl hydraulisch blockierbar als auch hydraulisch entlastbar sein muss.The Fig. 1 and 2 illustrate embodiments of at least one three-position spool control valve 3, 3 'containing hydraulic controls S, such as are used in vehicles, especially in agricultural vehicles, road service vehicles or the like .. Specially come for this hydraulic plows, snow plows, deep hole drills or similar devices with at least one load-moving hydraulic motor M, M 'in question, although the hydraulic control also has other applications, especially if a hydraulic motor M must be both hydraulically blocked and hydraulically relieved.

In der Ausführungsform in Fig. 1 bewegt der Hydromotor M, z.B. ein Differentialzylinder, eine Last L, die hier in Einfahrrichtung des Differentialzylinders wirkt. Die Last L kann beispielsweise ein Schneepflug, ein Hydraulikpflug oder ein Tieflochbohrer sein. Beide Arbeitsfluidseiten des Hydromotors M sind über Arbeitsleitungen 1, 2 an entsprechende Anschlüsse des Dreistellungs-Schiebersteuerventils 3 angeschlossen, in der gezeigten Ausführungsform, eines Dreistellungs-Druckregel-Schiebersteuerventils 3 (angedeutet durch die beiden parallelen Linien oberhalb und unterhalb des Symbolblocks). Das Dreistellungs-Schiebersteuerventil 3 ist an einem Druckanschluss 10 über eine Druckleitung 5 an eine Pumpe P (mit Rückschlagventil) und eine Dreiwege-Druckwaage 4 angeschlossen, und parallel dazu an ein Reservoir R. Die Dreiwege-Druckwaage 4 enthält einen Arbeitsströmungsweg 7, der zwischen Anschlüsse 12 und 9 einstellbar ist, und einen Arbeitsfluid-Abströmweg 11, der zwischen dem Anschluss 9 und einem Anschluss 8 einstellbar ist. Zwischenstellungen sind, wie bei einer Druckwaage üblich, ebenfalls einstellbar. In Fig. 1 ist die Druckwaage 4 in der Offenstellung gezeigt, in der der Arbeitsfluid-Strömungsweg 7 die Anschlüsse 12 und 9 verbindet, hingegen der Arbeitsfluid-Abströmweg 11 abgesperrt ist. Die Druckwaage 4 spielt zwischen der gezeigten Stellung und einer Absperrstellung, in der die Druckleitung 5 am Anschluss 12 abgesperrt ist, hingegen der Arbeitsfluid-Abströmweg 11 die Anschlüsse 9 und 8 zu einer Rücklaufleitung 6 und dem Reservoir R verbindet.In the embodiment in FIG Fig. 1 moves the hydraulic motor M, for example, a differential cylinder, a load L, which acts here in the retraction of the differential cylinder. The load L may be, for example, a snow plow, an hydraulic plow or a deep hole drill. Both working fluid sides of the hydraulic motor M are connected via working lines 1, 2 to corresponding ports of the three position spool control valve 3, in the embodiment shown, a three position pressure regulating spool control valve 3 (indicated by the two parallel lines above and below the symbol block). The three-position spool control valve 3 is connected to a pressure port 10 via a pressure line 5 to a pump P (with check valve) and a three-way pressure compensator 4, and parallel to a reservoir R. The three-way pressure compensator 4 includes a Arbeitsströmungsweg 7, the between Ports 12 and 9 is adjustable, and a Arbeitsfluid-Abströmweg 11, which is adjustable between the terminal 9 and a terminal 8. Intermediate positions are, as usual with a pressure compensator, also adjustable. In Fig. 1 the pressure compensator 4 is shown in the open position, in which the working fluid flow path 7 connects the ports 12 and 9, whereas the working fluid Abströmweg 11 is shut off. The pressure compensator 4 plays between the position shown and a shut-off position in which the pressure line 5 is shut off at the connection 12, whereas the working fluid outflow path 11 connects the connections 9 and 8 to a return line 6 and the reservoir R.

Die Druckwaage 4 wird in Stellrichtung zu der in Fig. 1 gezeigten Stellung durch eine Regelfeder 16 und an einem Steuerdruckanschluss 25 mit einem Lastdrucksignal beaufschlagt, das an einem Knoten 22 einer Lastdruck-Signalleitung 17 abgegriffen wird. In Richtung zur Absperrstellung wird die Druckwaage 4 an einem Steuerdruckanschluss 15 durch zwischen der Druckwaage 4 und dem Druckanschluss 10 abgegriffenen Steuerdruck aus einer Steuerleitung 13 und über eine Drossel 14 beaufschlagt. Die Lastdruck-Signalleitung 17 ist an ein Wechselventil 20 angeschlossen, das zwischen Lastdruck-Abgriffen 18, 19 z.B. der Arbeitsleitungen 1, 2 angeordnet ist.The pressure compensator 4 is in the direction of adjustment to the in Fig. 1 shown position by a control spring 16 and acted upon at a control pressure port 25 with a load pressure signal which is tapped at a node 22 of a load pressure signal line 17. In the direction of the shut-off position, the pressure compensator 4 is acted upon at a control pressure connection 15 by control pressure tapped between the pressure compensator 4 and the pressure connection 10 from a control line 13 and via a throttle 14. The load pressure signal line 17 is connected to a shuttle valve 20 which is arranged between load pressure taps 18, 19, for example, the working lines 1, 2.

Bei einer nicht gezeigten Alternative könnte die Lastdruck-Signalleitung 17 z.B. nur an den Abgriff 18 angeschlossen sein, und das Wechselventil 20 weggelassen werden.In an alternative not shown, the load pressure signal line 17 could be e.g. only be connected to the tap 18, and the shuttle valve 20 are omitted.

In der Lastdruck-Signalleitung 17 ist stromauf des Knotens 22 eine Drossel 21 vorgesehen. Vom Knoten 22 führt ein Zweig 17' der Lastdruck-Signalleitung zum Reservoir R. In dem Zweig 17' ist ein Proportionalmagnet-Ventil 23 enthalten, das, beispielsweise, normal durch eine Regelfeder und Druck in einer Vorsteuerleitung offengehalten ist, und bei bestromtem Proportionalmagneten 24 zu einer entsprechend proportionalen Absperr- oder Drosselstellung gebracht wird.In the load pressure signal line 17, a throttle 21 is provided upstream of the node 22. From node 22, a branch 17 'of the load pressure signal line leads to reservoir R. In branch 17' is included a proportional solenoid valve 23 which, for example, is normally kept open by a control spring and pressure in a pilot line and when proportional solenoid 24 is energized is brought to a corresponding proportional shut-off or throttle position.

Das Dreistellungs-Schiebersteuerventil 3 hat eine Neutralstellung 0 (wie gezeigt), in der der Hydromotor M hydraulisch blockiert ist. Das Dreistellungs-Schiebersteuerventil 3 lässt sich aus der Neutralstellung 0 in, z.B. druckregelnde, Steuerstellungen a, b verstellen, wobei in der Steuerstellung b aus dem Druckanschluss 10 die Arbeitsleitung 2 beaufschlagt und die Arbeitsleitung 1 zum Reservoir R entlastet sind, hingegen in der Steuerstellung a der Druckanschluss 10 mit der Arbeitsleitung 1 verbunden und die Arbeitsleitung 2 zum Reservoir R entlastet sind.The three-position spool control valve 3 has a neutral position 0 (as shown) in which the hydraulic motor M is hydraulically locked. The three-position spool control valve 3 is movable from the neutral position 0 in, e.g. druckregelnde, control positions a, b adjust, wherein in the control position b from the pressure port 10, the working line 2 and the working line 1 are relieved to the reservoir R, whereas in the control position a of the pressure port 10 connected to the working line 1 and the working line 2 to the reservoir R are relieved.

Über den Arbeitsfluid-Abströmweg 11 in der Druckwaage 4 und mit Hilfe des Proportionalmagnet-Ventils 23 ist sozusagen eine vierte Steuerstellung des Dreistellungs-Schiebersteuerventils 3 realisiert, in der in der jeweiligen Steuerstellung a, b über den einen Arbeitsfluid-Strömungsweg W die Arbeitsfluidseite des Hydromotors M aktiv zum Reservoir R entlastbar ist, die nicht ohnedies über das Dreistellungs-Schiebersteuerventil 3 zum Reservoir R entlastet ist. Dazu wird die Druckwaage 4 in ihre Absperrstellung verstellt, selbst bei laufender Pumpe P, in dem das Lastdrucksignal am Steuerdruckanschluss 25 über das Proportionalmagnet-Ventil 23 zum Reservoir R entlastet wird. Die Drossel 21 erzeugt ein Druckgefälle, so dass sich der Zweig 17' proportional entlasten lässt und auch der Hydromotor M an der unter Druck stehenden Arbeitsfluidseite in wählbarem Ausmaß entlastet wird. Die Druckwaage 4 leistet in diesem Fall eine feinfühlig regelbare Druckminderfunktion, da sie den Druck an der unter Druck stehenden Arbeitsfluidseite des Hydromotors M übe den dann auf Maximalgröße geöffneten Arbeitsfluid-Strömungsweg W stufenlos praktisch bis auf Null vermindern lässt (praktisch bis auf einen Druckwert von wenigen Bar, entsprechend der Kraft der Regelfeder 16 der Druckwaage 4).About the working fluid Abströmweg 11 in the pressure compensator 4 and with the aid of the proportional solenoid valve 23, so to speak, a fourth control position of the three-position valve control valve 3 is realized, in which in the respective control position a, b via the one working fluid flow path W, the working fluid side of the hydraulic motor M is actively relieved to the reservoir R, which is not already relieved via the three-position slide control valve 3 to the reservoir R. For this purpose, the pressure compensator 4 is adjusted to its shut-off position, even with the pump P running, in which the load pressure signal at the control pressure port 25 is relieved via the proportional solenoid valve 23 to the reservoir R. The throttle 21 generates a pressure gradient, so that the branch 17 'can be proportionally relieved and also the hydraulic motor M is relieved to the pressurized working fluid side in a selectable extent. The pressure compensator 4 makes in this case a finely adjustable pressure reducing function, since it allows the pressure at the pressurized working fluid side of the hydraulic motor M übe the then maximum open working fluid flow path W infinitely reduced practically to zero (practically up to a pressure value of a few Bar, according to the force of the control spring 16 of the pressure compensator 4).

Solange das Proportional-Magnetventil 23 der Entlastung E absperrt, arbeitet die Druckwaage 4 entsprechend den Drücken an den Anschlüssen 25, 15 nach Art eines Zulaufreglers, der in der Neutralstellung 0 den Druckanschluss 10 zum Reservoir R entlastet.As long as the proportional solenoid valve 23 shuts off the discharge E, the pressure compensator 4 operates according to the pressures at the terminals 25, 15 in the manner of an inlet regulator, which relieves the pressure port 10 to the reservoir R in the neutral position 0.

In der Ausführungsform in Fig. 2 hat das Dreistellungs-Schiebersteuerventil 3 (Regelventil) die Lastdrucksignalabgriffe 18, 19, wobei ein Schieberkolben 35 in der Steuerstellung a eine weitere fiktive Steuerstellung a1 einnehmen kann, in der ein Steuerdruck-Abströmweg 30 zum Reservoir R (über eine Steuerleitung 32) freigebbar ist, und z.B. die Arbeitsleitung 1 über den dann auf Maximalgröße geöffneten Arbeitsfluid-Strömungsweg W und die Druckwaage 4 entlastet wird. Da der Steuerdruck-Abströmweg 30 nur sehr kleinen Querschnitt benötigt und am Ende des Regelhubs bei Maximalgröße des Arbeitsfluid-Strömungsweges W offen ist, um nur den Steuerdruck des Lastdruck-Signalkreises abzubauen, wird der Regelhub der Steuerstellung a durch diese zusätzliche Funktion nicht spürbar verkleinert. Der Abströmweg 30 könnte alternativ durch einen kleinen Stellhub des Schieberkolbens 35 außerhalb des Regelhubs geöffnet werden.In the embodiment in FIG Fig. 2 the three-position spool control valve 3 (control valve) has the load pressure signal taps 18, 19, wherein a spool 35 in the control position a can assume a further fictitious control position a1 in which a control pressure outflow path 30 to the reservoir R (via a control line 32) is releasable, and, for example, the working line 1 is relieved of the then open to maximum size working fluid flow path W and the pressure compensator 4. Since the control pressure Abströmweg 30 requires only very small cross-section and at the end of the control stroke at maximum size of the working fluid flow path W is open to reduce only the control pressure of the load pressure signal circuit, the control stroke of the control position a is not noticeably reduced by this additional function. The Abströmweg 30 could alternatively be opened by a small adjusting stroke of the spool 35 outside the control stroke.

Die Lastdruckabgriffe 18, 19 in den Arbeitsleitungen 1, 2 sind jeweils über Steuerdruckkanäle 26, 27 in den jeweiligen Steuerstellungen a, b mit einem Lastdrucksignalkreis 28 verbindbar, der über die Drossel 21 zum Steuerdruckanschluss 25 der Druckwaage 4 führt. In der Neutralstellung 0 (hydraulische Blockierung des Hydromotors M) ist der Lastdruck-Signalkreis 28 über einen Steuerdruckkanal 29 im Dreistellungs-Schiebersteuerventil 3 und die Steuerleitung 32 zum Reservoir R entlastet.The load pressure taps 18, 19 in the working lines 1, 2 are each connected via control pressure channels 26, 27 in the respective control positions a, b with a load pressure signal circuit 28 which leads via the throttle 21 to the control pressure port 25 of the pressure compensator 4. In the neutral position 0 (hydraulic locking of the hydraulic motor M), the load pressure signal circuit 28 is relieved via a control pressure channel 29 in the three-position slide control valve 3 and the control line 32 to the reservoir R.

Um, beispielsweise bei laufender Pumpe P, den hydraulisch blockierten Hydromotor M (erhöhter Druck in der Arbeitsleitung 1) über die Arbeitsleitung 1 zu entlasten, wird das Dreistellungs-Schiebersteuerventil 3 in die zusätzliche Steuerstellung a1 gebracht, in der das Lastdrucksignal über den Steuerkanal 30 zum Reservoir R entlastet wird. Mit Verschwinden des Steuerdrucks am Steuerdruckanschluss 25 der Druckwaage 4 wird diese in ihre Absperrstellung gebracht, in der der Arbeitsfluid-Abströmweg 11 zum Reservoir R geöffnet ist und die Arbeitsleitung 1 über den Arbeitsfluid-Abströmweg 11 mit großem Querschnitt entlastet wird. Die Arbeitsleitung 2 ist in der Steuerstellung a1 ohnedies mit dem Reservoir R verbunden. Der Hydromotor M wird auf diese Weise in eine Schwimmstellung gebracht.In order to relieve, for example, when running pump P, the hydraulically blocked hydraulic motor M (increased pressure in the working line 1) via the working line 1, the three-position slide control valve 3 is brought into the additional control position a1, in which the load pressure signal via the control channel 30 for Reservoir R is relieved. With the disappearance of the control pressure at the control pressure port 25 of the pressure compensator 4, this is brought into its shut-off position in which the Arbeitsfluid-Abströmweg 11 is opened to the reservoir R and the working line 1 is relieved via the Arbeitsfluid-Abströmweg 11 with a large cross-section. The working line 2 is in the control position a1 anyway connected to the reservoir R. The hydraulic motor M is brought in this way in a floating position.

Als mögliche Option weist die Hydrauliksteuerung S in Fig. 2 einen weiteren, über Arbeitsleitungen 1', 2' betätigbaren Hydromotor M' und ein parallel geschaltetes weiteres Dreistellungs-Schiebersteuerventil 3' (mit absperrender Neutralstellung 0' und Sekundär-Druckbegrenzungen B1', B2') auf. Der weitere Hydromotor M' ist z.B. mit dem Hydromotor M gekoppelt oder koppelbar, um den Hydromotor M bei entlasteten Arbeitsleitungen 1, 2 (z.B. in der Steuerstellung a1 des Dreistellungs-Steuerventils 3, d.h. in einer Schwimmstellung) verstellen zu können.As a possible option, the hydraulic control S in Fig. 2 a further, via working lines 1 ', 2' operable hydraulic motor M 'and a parallel connected further three-position slide control valve 3 '(with shut-off neutral position 0' and secondary pressure limitations B1 ', B2'). The further hydraulic motor M 'is for example coupled to the hydraulic motor M or coupled to the hydraulic motor M at unloaded working lines 1, 2 (eg in the control position a1 of the three-position control valve 3, ie in a floating position) to adjust.

In der Ausführungsform in Fig. 2 sind als weitere Option zusätzlich zu dem Dreistellungs-Schiebersteuerventil 3 Sekundärdruckbegrenzungen B1, B2 (oder zumindest die Sekundärdruckbegrenzung B1 für die Arbeitsleitung 1) im Lastdrucksignalkreis 28 vorgesehen, deren Zweck es grundsätzlich ist, die Maximaldrücke in den Arbeitsleitungen 1, 2 über die Druckwaage 4 (Zulaufregler) zu begrenzen (gegebenenfalls auf unterschiedliche Druckwerte). Da die Sekundärdruckbegrenzungen B1 und B2 identisch aufgebaut sind, wird nur die Sekundärdruckbegrenzung B1 erläutert.In the embodiment in FIG Fig. 2 are as a further option in addition to the three-position slide control valve 3 secondary pressure B1, B2 (or at least the secondary pressure limitation B1 for the working line 1) provided in the load pressure signal circuit 28 whose purpose is in principle, the maximum pressures in the working lines 1, 2 via the pressure compensator 4 Flow regulator) (possibly to different pressure values). Since the secondary pressure limitations B1 and B2 are constructed identically, only the secondary pressure limitation B1 is explained.

Die Sekundärdruckbegrenzung B1 ist in der Steuerstellung a des Kolbenschiebers 35 über einen Kurzschlusskanal 36 mit dem Lastdruck-Signalkreis 28 verbunden und enthält ein vorgesteuertes Druckbegrenzungsventil 33, das druckabhängig zum Reservoir R öffnet. Zur wahlweisen Druckentlastung (alternativ zur Steuerstellung a1 oder sogar additiv zu der Steuerstellung a1) ist ein Proportionalmagnet-Sitzventil 34 vorgesehen, wobei das Lastdrucksignal nicht nur am Steuerdruckanschluss 25 der Druckwaage 4 sondern auch am Druckbegrenzungsventil 33 und dem Proportionalmagnet-Sitzventil 34 ansteht. Das vorgesteuerte Druckbegrenzungsventil 33 begrenzt eine maximale Höhe des Lastdrucksignals. Das Proportionalmagnet-Sitzventil 34 ist dank Vorsteuerung, und gegebenenfalls auch durch eine Feder in die gezeigte Durchgangsstellung bringbar und wird durch den Proportionalmagneten 24 proportional in eine Absperrstellung verstellt. Das Proportionalmagnet-Sitzventil 34 ist, z.B., grundsätzlich zum Erzielen einer Sicherheitsfunktion in der Sekundärdruckbegrenzung B1 vorgesehen, beispielsweise um das Lastdrucksignal bei Bedarf vollständig abzubauen und die Druckwaage 4 in die Absperrstellung zu bringen, so dass der Hydromotor M nicht mehr gegen die Last L zu bewegen ist. Das Proportionalmagnet-Sitzventil 34 wird hier in Kombination mit der Druckwaage 4 dazu benutzt, die Arbeitsleitung 1 des Hydromotors M wahlweise zu entlasten.The secondary pressure limitation B1 is connected in the control position a of the spool 35 via a short-circuit channel 36 with the load pressure signal circuit 28 and includes a pilot-operated pressure relief valve 33 which opens pressure-dependent to the reservoir R. For optional pressure relief (alternatively to the control position a1 or even additive to the control position a1), a proportional solenoid seat valve 34 is provided, wherein the load pressure signal is present not only at the control pressure port 25 of the pressure compensator 4 but also on the pressure relief valve 33 and the proportional solenoid seat valve 34. The pilot-operated pressure limiting valve 33 limits a maximum height of the load pressure signal. The proportional solenoid seat valve 34 is due to pilot control, and optionally also by a spring in the passage position shown can be brought and is adjusted proportionally by the proportional solenoid 24 in a shut-off position. The proportional solenoid seat valve 34 is, for example, basically provided to achieve a safety function in the secondary pressure limitation B1, for example, to completely reduce the load pressure signal as needed and bring the pressure compensator 4 in the shut-off, so that the hydraulic motor M no longer against the load L. is moving. The proportional solenoid seat valve 34 is here used in combination with the pressure compensator 4 to selectively relieve the working line 1 of the hydraulic motor M.

Hierzu wird zunächst bei beispielsweise in die Steuerstellung a verstelltem Dreistellungs-Schiebersteuerventil 3 der Proportionalmagnet 24 entstromt, so dass das Lastdrucksignal abgebaut wird und die Druckwaage 4 ihre Absperrstellung einnimmt. In der Steuerstellung a werden die Arbeitsleitung 1 aktiv über den Arbeitsfluid-Abströmweg 11 in der Druckwaage 4 und die Arbeitsleitung 2 ohnedies jeweils mit dem Reservoir R verbunden, so dass der Hydromotor M in eine Schwimmstellung gelangt. Der Proportionalmagnet 24 ermöglicht es, das Ausmaß der Verminderung des Lastdrucksignals exakt zu steuern, z.B. mit einer milden Rampenfunktion oder nur bis auf einen bestimmten Druckwert.For this purpose, the proportional solenoid 24 is first de-energized at, for example, in the control position a verstelltem three-position slide control valve 3, so that the load pressure signal is reduced and the pressure compensator 4 assumes its shut-off position. In the control position a, the working line 1 becomes active via the working fluid outflow path 11 in the pressure compensator 4 and the working line 2 in each case in each case connected to the reservoir R, so that the hydraulic motor M enters a floating position. The proportional solenoid 24 makes it possible to accurately control the degree of reduction of the load pressure signal, eg with a mild ramp function or only up to a certain pressure value.

Ist der Hydromotor M' vorgesehen, kann er dann den Hydromotor M nach Bedarf verstellen, beispielsweise über eine Kopplung K zwischen den beiden Hydromotoren M, M'. Wie gesagt, können beide Entlastungsmöglichkeiten von Fig. 2 vorgesehen sein und benutzt werden, oder nur eine (d.h. entweder die Steuerstellung a1 und eine oder zwei Sekundär-Druckbegrenzungen B1, B2 mit den Sitzventilen 34, 34', oder nur die Steuerstellung a1 oder nur eine oder beide Sekundär-Druckbegrenzungen B1, B2. Alternativ oder additiv könnte für die Steuerstellung b eine weitere Steuerstellung b1 (nicht gezeigt) analog wie zur Steuerstellung a1 erläutert, mit dem Arbeitsfluid-Strömungsweg W in Maximalgröße vorgesehen sein.If the hydraulic motor M 'provided, he can then adjust the hydraulic motor M as needed, for example via a coupling K between the two hydraulic motors M, M'. As I said, both relief possibilities of Fig. 2 be provided and used, or only one (ie either the control position a1 and one or two secondary pressure limitations B1, B2 with the seat valves 34, 34 ', or only the control position a1 or only one or both secondary pressure limitations B1, B2. Alternatively or additionally, another control position b1 (not shown) for the control position b could be analogously explained as for the control position a1, with the working fluid flow path W being provided in maximum size.

Claims (14)

Hydrauliksteuerung (S) für zumindest einen Hydromotor (M) zum Bewegen einer Last (L), insbesondere in einem Fahrzeug, mit einem in einem Arbeitsfluidkreis zwischen dem Hydromotor (M) und einer einem Reservoir (R) zugeordneten Pumpe (P) eingeschalteten Dreistellungs-Schiebersteuerventil (3) mit absperrender Neutralstellung (0), wobei zwischen der Pumpe (P) und einem Pumpenanschluss (10) des Dreistellungs-Schiebersteuerventils eine an einen Lastdruck-Signalkreis (28) des Dreistellungs-Schiebersteuerventils angeschlossene Druckwaage (4) angeordnet ist, die vom Druck im Pumpenanschluss (10) entgegengesetzt zum Lastdrucksignal in eine die Pumpe (P) isolierende Absperrstellung bringbar ist, dadurch gekennzeichnet, dass die Druckwaage (4) mit einem Arbeitsfluid-Abströmweg (11) zum Reservoir (R) ausgebildet ist, der in der Absperrstellung der Druckwaage (4) den Druckanschluss (10) mit dem Reservoir (R) verbindet, und dass zum gewollten Entlasten des Hydromotors (M) über den Arbeitsfluid-Abströmweg (11) in der Druckwaage (4) der Lastdruck-Signalkreis (28) wahlweise zum Reservoir (R) entlastbar ist.Hydraulic control (S) for at least one hydraulic motor (M) for moving a load (L), in particular in a vehicle, with a three-position switch activated in a working fluid circuit between the hydraulic motor (M) and a pump (P) associated with a reservoir (R). Valve control valve (3) with shut-off neutral position (0), wherein between the pump (P) and a pump port (10) of the three-position spool control valve to a load pressure signal circuit (28) of the three-position spool control valve connected pressure compensator (4) is arranged from the pressure in the pump connection (10) opposite to the load pressure signal in a the pump (P) insulating shutoff position can be brought, characterized in that the pressure compensator (4) with a working fluid Abströmweg (11) to the reservoir (R) is formed in the Shut-off position of the pressure compensator (4) connects the pressure port (10) with the reservoir (R), and that for intentional unloading of the hydraulic motor (M) via the working fluid Abs flow path (11) in the pressure compensator (4) of the load pressure signal circuit (28) optionally to the reservoir (R) is relieved. Hydrauliksteuerung nach Anspruch 1, dadurch gekennzeichnet, dass der Lastdruck-Signalkreis (28) wahlweise über wenigstens einen in einer Steuerstellung (a1) des Dreistellungs-Schiebersteuerventils (3) freigebbaren Steuerdruck-Abströmweg (30) im Dreistellungs-Schiebersteuerventil (3) zum Reservoir (R) entlastbar ist.Hydraulic control according to claim 1, characterized in that the load pressure signal circuit (28) selectively via at least one in a control position (a1) of the three-position slide control valve (3) releasable Steuerdruck-Abströmweg (30) in three-position slide control valve (3) to the reservoir ( R) is relieved. Hydrauliksteuerung nach Anspruch 1, dadurch gekennzeichnet, dass der Lastdruck-Signalkreis (28) wahlweise über eine zwischen dem Reservoir (R) und dem Dreistellungs-Schiebesteuerventil (3) angeordnete Sekundärdruckbegrenzung (B1, B2) des Hydromotors (M) zum Reservoir (R) entlastbar ist.Hydraulic control according to claim 1, characterized in that the load pressure signal circuit (28) optionally via a between the reservoir (R) and the three-position shift control valve (3) arranged secondary pressure limitation (B1, B2) of the hydraulic motor (M) to the reservoir (R) is relieved. Hydrauliksteuerung nach Anspruch 1, dadurch gekennzeichnet, dass der Lastdruck-Signalkreis (28) wahlweise über eine zwischen dem Hydromotor (M) und dem Reservoir (R) angeordnete Entlastungsvorrichtung (E) entlastbar ist.Hydraulic control according to claim 1, characterized in that the load pressure signal circuit (28) is optionally relieved via a between the hydraulic motor (M) and the reservoir (R) arranged discharge device (E). Hydrauliksteuerung nach wenigstens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Lastdruck-Signalkreis (28) proportional entlastbar ist.Hydraulic control according to at least one of the preceding claims, characterized in that the load pressure signal circuit (28) is proportionally relieved. Hydrauliksteuerung nach wenigstens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass mit der den Arbeitsfluid-Abströmweg (11) aufweisenden Druckwaage (4) eine Druckminderfunktion bis auf einen von einer Regelfeder (16) der Druckwaage (4) begrenzten Minimaldruck erzeugbar ist.Hydraulic control according to at least one of the preceding claims, characterized in that with the working fluid Abströmweg (11) having pressure compensator (4) a pressure reducing function can be generated except for a minimum pressure limited by a control spring (16) of the pressure compensator (4). Hydrauliksteuerung nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass in der Sekundärdruckbegrenzung (B1, B2) oder der Entlastungsvorrichtung (E) zum Entlasten des Lastdrucksignals für die Druckwaage (4) ein Proportionalmagnet-Ventil (34, 23), insbesondere ein Proportionalmagnet-Sitzventil (34), stromab einer Drossel (21) vorgesehen ist, und dass das Lastdrucksignal für die Druckwaage (4) zwischen der Drossel (21) und dem Proportionalmagnet-Ventil (34, 23) von einem Lastdrucksignal des Hydromotors (M) abgegriffen wird.Hydraulic control according to claim 3 or 4, characterized in that in the secondary pressure limitation (B1, B2) or the discharge device (E) for relieving the load pressure signal for the pressure compensator (4) a proportional solenoid valve (34, 23), in particular a proportional solenoid seat valve (34), downstream of a throttle (21) is provided, and that the load pressure signal for the pressure compensator (4) between the throttle (21) and the proportional solenoid valve (34, 23) from a load pressure signal of the hydraulic motor (M) is tapped. Hydrauliksteuerung nach wenigstens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Dreistellungs-Steuerventil (3) ein Druckregel-Steuerventil ist, dass der Steuerdruck-Abströmweg (30) in einem Kolbenschieber (35) in zumindest einer Steuerstellung (a, a1) am Ende oder außerhalb des Regelhubs des Kolbenschiebers (35) platziert ist, und dass der Steuerdruck-Abströmweg (30) mit einer Stellbewegung des Kolbenschiebers (35) erheblich kleiner als der Regelhub in der Steuerstellung (a, a1) freigebbar ist.Hydraulic control according to at least one of the preceding claims, characterized in that the three-position control valve (3) is a pressure regulating control valve, that the control pressure Abströmweg (30) in a piston slide (35) in at least one control position (a, a1) at the end or outside the control stroke of the spool (35) is placed, and that the control pressure Abströmweg (30) with an actuating movement of the spool (35) is considerably smaller than the control stroke in the control position (a, a1) is releasable. Hydrauliksteuerung nach Anspruch 8, dadurch gekennzeichnet, dass in dem als Druckregel-Steuerventil ausgebildeten Dreistellungs-Steuerventil (3) die Steuerstellung (a, b) je einen endlichen Regelhub definiert, innerhalb dessen ein Arbeitsfluid-Strömungsweg (W) graduell zunehmend bis zu einer Maximalgröße aufsteuerbar ist, und dass der zusätzliche Steuerdruck-Abströmweg (30) innerhalb des Regelhubs in Stellrichtung zur Maximalgröße am Ende des Regelhubs oder anschließend (zusätzliche fiktive Steuerstellung (a1) an den Regelhub platziert ist.Hydraulic controller according to claim 8, characterized in that in the three-position control valve (3) designed as a pressure control control valve, the control position (a, b) each defines a finite control stroke, within which a working fluid flow path (W) gradually increases gradually up to a maximum size can be controlled, and that the additional control pressure Abströmweg (30) within the Regelhubs in the direction of adjustment to the maximum size at the end of the Regelhubs or subsequently (additional fictitious control position (a1) is placed on the control stroke. Hydrauliksteuerung nach wenigstens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Hydromotor (M) mit einem weiteren Hydromotor (M') gekoppelt oder koppelbar und nach wahlweiser aktiver Druckentlastung an beiden Arbeitsfluidseiten mittels des weiteren Hydromotors (M') verstellbar ist.Hydraulic control according to at least one of the preceding claims, characterized in that the hydraulic motor (M) with another hydraulic motor (M ') coupled or coupled and after optional active pressure relief at both working fluid sides by means of the further hydraulic motor (M') is adjustable. Hydrauliksteuerung nach Anspruch 3, dadurch gekennzeichnet, dass die Sekundärdruckbegrenzung (B1, B2) für zumindest eine Arbeitsfluidseite des Hydromotors (M), vorzugsweise für beide Arbeitsfluidseiten des Hydromotors (M), vorgesehen ist.Hydraulic control according to claim 3, characterized in that the secondary pressure limitation (B1, B2) is provided for at least one working fluid side of the hydraulic motor (M), preferably for both working fluid sides of the hydraulic motor (M). Hydrauliksteuerung nach Anspruch 4, dadurch gekennzeichnet, dass die Entlastungsvorrichtung (E) in einer Lastdrucksignalleitung (17, 17') angeordnet ist, die an zumindest eine Arbeitsfluidseite des Hydromotors (M) angeschlossen ist, vorzugsweise über ein Wechselventil (20) lastdrucksignalabhängig an jede Arbeitsfluidseite des Hydromotors (M) anschließbar ist.Hydraulic controller according to claim 4, characterized in that the discharge device (E) in a load pressure signal line (17, 17 ') is arranged, which is connected to at least one working fluid side of the hydraulic motor (M), preferably via a shuttle valve (20) loaddrucksignalabhängig to each working fluid side of the hydraulic motor (M) can be connected. Hydrauliksteuerung nach wenigstens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass diejenige Arbeitsfluidseite des Hydromotors (M) über die Druckwaage (4) zum Reservoir entlastbar ist, die in der Steuerstellung (a, b, a1) des Dreistellungs-Schiebersteuerventils (3) nicht ohnehin zum Reservoir (R) entlastet ist.Hydraulic control according to at least one of the preceding claims, characterized in that that working fluid side of the hydraulic motor (M) via the pressure compensator (4) to the reservoir is relieved, in the control position (a, b, a1) of the three-position valve control valve (3) not anyway to the reservoir (R) is relieved. Hydrauliksteuerung nach wenigstens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Druckwaage (4) mittels einer aktiven Entlastung des Lastdrucksignals als proportionaler Zulaufregler betreibbar ist.Hydraulic control according to at least one of the preceding claims, characterized in that the pressure compensator (4) can be operated by means of an active relief of the load pressure signal as a proportional inlet regulator.
EP20080014795 2008-08-20 2008-08-20 Hydraulic device for a hydro motor Active EP2157320B1 (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3018364A1 (en) * 2014-11-10 2016-05-11 HAWE Hydraulik SE Control device and sliding piston
US11841716B2 (en) 2020-12-28 2023-12-12 Danfoss Power Solutions (Zhejiang) Co. Ltd. Load-sensing multi-way valve work section
CN113882444A (en) * 2021-10-29 2022-01-04 徐州徐工挖掘机械有限公司 Bulldozing hydraulic system and excavator with dozing blade function of floating

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EP2157320B1 (en) 2010-12-08

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