EP2157320A1 - Commande hydraulique pour un moteur hydraulique - Google Patents

Commande hydraulique pour un moteur hydraulique 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)
English (en)
Other versions
EP2157320B1 (fr
Inventor
Martin Heusser
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hawe Hydraulik SE
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Hawe Hydraulik SE
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Publication date
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Priority to EP20080014795 priority Critical patent/EP2157320B1/fr
Priority to DE200850002003 priority patent/DE502008002003D1/de
Publication of EP2157320A1 publication Critical patent/EP2157320A1/fr
Application granted granted Critical
Publication of EP2157320B1 publication Critical patent/EP2157320B1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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)
EP20080014795 2008-08-20 2008-08-20 Commande hydraulique pour un moteur hydraulique Active EP2157320B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP20080014795 EP2157320B1 (fr) 2008-08-20 2008-08-20 Commande hydraulique pour un moteur hydraulique
DE200850002003 DE502008002003D1 (de) 2008-08-20 2008-08-20 Hydrauliksteuerung für einen Hydromotor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20080014795 EP2157320B1 (fr) 2008-08-20 2008-08-20 Commande hydraulique pour un moteur hydraulique

Publications (2)

Publication Number Publication Date
EP2157320A1 true EP2157320A1 (fr) 2010-02-24
EP2157320B1 EP2157320B1 (fr) 2010-12-08

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Application Number Title Priority Date Filing Date
EP20080014795 Active EP2157320B1 (fr) 2008-08-20 2008-08-20 Commande hydraulique pour un moteur hydraulique

Country Status (2)

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EP (1) EP2157320B1 (fr)
DE (1) DE502008002003D1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3018364A1 (fr) * 2014-11-10 2016-05-11 HAWE Hydraulik SE Dispositif de commande et piston coulissant
CN113882444A (zh) * 2021-10-29 2022-01-04 徐州徐工挖掘机械有限公司 一种带有推土铲浮动功能的推土液压系统以及挖掘机
US11841716B2 (en) 2020-12-28 2023-12-12 Danfoss Power Solutions (Zhejiang) Co. Ltd. Load-sensing multi-way valve work section

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0603722A1 (fr) * 1992-12-23 1994-06-29 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Dispositif de commande hydraulique
EP1058010A1 (fr) * 1998-12-28 2000-12-06 Hitachi Construction Machinery Co., Ltd. Entrainement hydraulique
CA2552060A1 (fr) * 2005-07-21 2007-01-21 Deere & Company Servocommande sensible a la charge

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0603722A1 (fr) * 1992-12-23 1994-06-29 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Dispositif de commande hydraulique
EP1058010A1 (fr) * 1998-12-28 2000-12-06 Hitachi Construction Machinery Co., Ltd. Entrainement hydraulique
CA2552060A1 (fr) * 2005-07-21 2007-01-21 Deere & Company Servocommande sensible a la charge

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3018364A1 (fr) * 2014-11-10 2016-05-11 HAWE Hydraulik SE Dispositif de commande et piston coulissant
US11841716B2 (en) 2020-12-28 2023-12-12 Danfoss Power Solutions (Zhejiang) Co. Ltd. Load-sensing multi-way valve work section
CN113882444A (zh) * 2021-10-29 2022-01-04 徐州徐工挖掘机械有限公司 一种带有推土铲浮动功能的推土液压系统以及挖掘机

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DE502008002003D1 (de) 2011-01-20
EP2157320B1 (fr) 2010-12-08

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