EP1659087A2 - Arrangement hydraulique - Google Patents

Arrangement hydraulique Download PDF

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Publication number
EP1659087A2
EP1659087A2 EP05111001A EP05111001A EP1659087A2 EP 1659087 A2 EP1659087 A2 EP 1659087A2 EP 05111001 A EP05111001 A EP 05111001A EP 05111001 A EP05111001 A EP 05111001A EP 1659087 A2 EP1659087 A2 EP 1659087A2
Authority
EP
European Patent Office
Prior art keywords
hydraulic
pressure
line
control pressure
hydraulic cylinder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP05111001A
Other languages
German (de)
English (en)
Other versions
EP1659087A3 (fr
Inventor
Marcus Bitter
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.)
Deere and Co
Original Assignee
Deere and Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Deere and Co filed Critical Deere and Co
Publication of EP1659087A2 publication Critical patent/EP1659087A2/fr
Publication of EP1659087A3 publication Critical patent/EP1659087A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/021—Installations or systems with accumulators used for damping
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/065—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks non-masted
    • B66F9/0655—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks non-masted with a telescopic boom
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/20—Means for actuating or controlling masts, platforms, or forks
    • B66F9/22—Hydraulic devices or systems
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • E02F9/2207—Arrangements for controlling the attitude of actuators, e.g. speed, floating function for reducing or compensating oscillations
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
    • E02F9/2228—Control of flow rate; Load sensing arrangements using pressure-compensating valves including an electronic controller
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F15B11/0445—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out" with counterbalance valves, e.g. to prevent overrunning or for braking
    • 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
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance 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
    • F15B2211/625—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/8616—Control during or prevention of abnormal conditions the abnormal condition being noise or vibration
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/863—Control during or prevention of abnormal conditions the abnormal condition being a hydraulic or pneumatic failure

Definitions

  • the invention relates to a hydraulic arrangement for a suspension system, comprising a hydraulic cylinder, a filling pressure generating means, a hydraulic tank, a controller connected to the conveyor and the hydraulic tank, a first line connecting the controller to a first chamber of the hydraulic cylinder, one in the first Line arranged load holding device and connected to the first line hydraulic accumulator.
  • a hydraulic suspension system that cushions the boom or the rocker to achieve overall on the vehicle improved suspension comfort, especially while driving.
  • the lifting side of a hydraulic cylinder is connected to a hydraulic accumulator to effect a suspension through the hydraulic accumulator.
  • the lowering side of the hydraulic cylinder is connected to a hydraulic tank to prevent on the one hand cavitation on the lower side and on the other to allow free movement of the piston rod during the suspension process.
  • these suspension systems to protect the hydraulic cylinder against hose breaks, be provided with load-holding devices.
  • a hydraulic arrangement for such a suspension system is disclosed in EP 1 157 963 A2. It is proposed a suspension system for the boom of a telehandler, which provides a load-holding device to secure a pressure drop in a hydraulic cylinder and in a hydraulic accumulator.
  • the load-holding device essentially comprises a check valve, which can be bypassed in combination with a controllable pressure relief valve by the pressure relief valve is brought by means of control pressure lines from a closed normal position to an open position.
  • the load-holding device is arranged on the supply side in front of the hydraulic cylinder and the hydraulic accumulator.
  • the disadvantage is that thereby only a load-holding device for securing two pressure-loaded hydraulic components is provided. A pipe break occurring between the hydraulic cylinder and the hydraulic accumulator would lead to a drop of the boom and is thus not secured by the load-holding device.
  • the object underlying the invention is seen to provide a hydraulic arrangement of the type mentioned, which makes it possible to ensure a separate protection of the hydraulic cylinder and the hydraulic accumulator, while providing a suspension function.
  • a hydraulic arrangement of the type mentioned is designed such that in the first line between the load holding device and the control device, a first switching valve is arranged, the hydraulic accumulator between the load holding device and the first switching valve is connected to the first line and the load holding device and the first Switching valve are controlled synchronously independently of a filling pressure of the hydraulic cylinder, wherein the load holding device can be brought from an opening in the direction of the control unit to an opening position and the first switching valve from an opening to a closing in the direction of the controller position.
  • the first switching valve between the hydraulic accumulator and the control unit and the load-holding device between the hydraulic accumulator and the hydraulic cylinder are arranged a separate fuse of the hydraulic cylinder and the hydraulic accumulator is ensured.
  • the first switching valve is designed such that it closes leak-free in the direction of the control device in the closing position. Furthermore, the fact that the switching valve and the load-holding device are synchronously switchable such that an opening of the load-holding device is connected to a closure of the first switching valve, ensures that a suspension function can be performed by the hydraulic accumulator for the hydraulic cylinder.
  • the hydraulic arrangement is provided with a hydraulic control pressure device, which is fed by means of a control pressure generating conveyor.
  • a control pressure line for hydraulically switched valves is connected via a control pressure valve either with the conveyor or the hydraulic tank. It is conceivable, several To arrange control pressure lines, which can be operated independently of each other via further control pressure valves, so that a plurality of hydraulically switchable switching valves are independently switchable. For example, then the load-holding device and the first switching valve can be controlled via independent control pressure lines.
  • pressure-controlled means in the form of a shuttle valve are provided.
  • the shuttle valve is connected on one input side to a first control pressure line of the control pressure device and on another input side to a second control pressure line connected to a chamber of the hydraulic cylinder. According to the pressure occurring in the control pressure lines, the shuttle valve is thereby fed either on the hydraulic cylinder side or on the control pressure device side.
  • the shuttle valve is connected to a second chamber of the hydraulic cylinder.
  • the first switching valve is preferably connected to the control pressure device via a third control pressure line, which branches off from the first control pressure line. This ensures that the first switching valve and the pressure-controlled means are substantially simultaneously or parallel controlled.
  • the trained as a shuttle valve pressure-controlled means are on the output side via a fourth control pressure line connected to the load-holding device, so that the load-holding device can be controlled or opened, for example, via the pressure acting in the second chamber of the hydraulic cylinder or the pressure generated by the control pressure device.
  • the load holding device Via a fifth control pressure line, which is connected to the first chamber of the hydraulic cylinder, the load holding device can be controlled via the pressure acting in the first chamber. This ensures that the load-holding device opens when, for example, a pressure overloading the hydraulic cylinder is reached (for example due to excessively high loads), so that hydraulic fluid can flow out of the first chamber in a controlled manner.
  • a second switching valve is provided, which can be brought into an opening or in a one-sided or bilateral closing position.
  • the hydraulic accumulator can be connected via the second switching valve so that the hydraulic cylinder can spring when the load holding device is open.
  • the second switching valve is designed such that it closes leak-free, wherein it closes in a one-sided closing position only in the direction of the hydraulic accumulator.
  • one-sided closing training of the second switching valve ensures that a pressure equalization can be done by the hydraulic accumulator.
  • a pressure relief valve having a line which can be arranged between the second switching valve and the hydraulic accumulator, an additional hedge of the hydraulic accumulator can be done.
  • the line connects the hydraulic accumulator with the Hydraulic tank.
  • pressure peaks occurring in the hydraulic accumulator for example, which can occur when the hydraulic cylinder is subjected to excessive suspension movements, can be reduced.
  • the hydraulic accumulator is protected against overpressure by the overpressure valve. Similar arrangements are available, for example, to secure the conveyor against over-pressure.
  • the hydraulic arrangement is provided with a second line which connects the control unit to the second chamber.
  • a second line By a second line, the hydraulic cylinder can be pressurized on both sides, so that a controlled by the control unit pressurized lifting and lowering of the hydraulic cylinder is made possible.
  • a third conduit provided with a third switching valve communicating with the second chamber and the hydraulic tank allows drainage of hydraulic fluid from the second chamber of the hydraulic cylinder independently of the position of the controller.
  • a third switching valve By opening the third switching valve, for example, in a neutral position of the controller (first and second line are closed) a spring movement of the hydraulic cylinder in both directions, without on the one hand, a negative pressure in the second chamber (descent spring movement) and on the other hand, a spring-locking overpressure in the second chamber (ascending spring movement) can adjust.
  • the third switching valve can be closed.
  • the first chamber of the hydraulic cylinder can advantageously be brought into communication with the hydraulic accumulator via a fourth line.
  • the fourth line is preferably provided with a check valve which closes leak-free in the direction of the hydraulic accumulator.
  • pressure equalization can take place on the part of the hydraulic accumulator, resulting in advantages in the suspension function (a jerky lifting of the hydraulic cylinder when the suspension function is switched on is avoided).
  • the second switching valve should be designed such that it closes leak-free in the closed position in both directions.
  • a sensor In order to check whether the hydraulic cylinder is in a preferred position for activation of the suspension, for example in a fully lowered position, a sensor may be provided.
  • the sensor can be designed as a contact switch or angle sensor with the movement of the hydraulic cylinder and is thus coupled with its position. Depending on the sensor, the suspension function can then be released or blocked.
  • a pressure sensor or pressure switch may be provided. Depending on the sensor or switch, the suspension function can then be released or blocked.
  • one or more switching valves can be controlled.
  • the load-holding device and the first switching valve are controlled via the first control pressure line and via the shuttle valve, so that a synchronous circuit is ensured here.
  • other switching valves such as. B. the second and the third switching valve are controlled via the first control pressure line, so that by switching the first control pressure valve, the load holding device and the first to third switching valve are synchronously switchable.
  • the load holding device and the first switching valve via the first control pressure line or via the first control pressure valve and the second and third switching valve via a second control pressure line or via a second control pressure valve be controlled.
  • other drive combinations and variants are conceivable.
  • one or more switching valves may be electrically energized.
  • the load holding device and the first switching valve are controlled via the control pressure device, wherein the first control pressure valve and the second and third switching valve are electrically switched.
  • the suspension is then activated by electrically switching the first control pressure valve and the second and third switching valves.
  • an electronic control unit or an electrical control unit can be used.
  • the pressure compensation device provides pressure equalization of the hydraulic accumulator with the first chamber of the hydraulic cylinder by providing a line provided with a non-return valve opening in the direction of the hydraulic accumulator, which line is arranged parallel to a pressure compensator.
  • the pressure compensator is controlled as a function of the pressure prevailing in the hydraulic cylinder and in the hydraulic accumulator.
  • Such pressure compensation devices are state of the art and are offered for example by the company HYDAC.
  • the conveying means generating a control pressure and the conveying means generating a filling pressure may be a common or two or more separate conveying means.
  • designed as a hydraulic pump conveying means may be designed and arranged such that on the one hand, a filling pressure for the hydraulic accumulator and on the other hand via a pressure control means, for example via a pressure accumulator, which always provides a constant control pressure and is charged via the conveyor, also a control pressure for Control pressure device supplies.
  • a pressure control means for example via a pressure accumulator, which always provides a constant control pressure and is charged via the conveyor, also a control pressure for Control pressure device supplies.
  • FIG. 1 hydraulic arrangement 10 shows an inventive embodiment for the realization of a suspension.
  • the hydraulic assembly 10 includes a switchable via an actuator 11 control unit 12, for example, a slide valve, which is connected via hydraulic lines 14, 16 with a conveyor 18, such as a hydraulic pump, and a hydraulic tank 20, wherein the control unit 12 preferably in three operating positions, lifting -, Neutral and Senk ein, is switchable.
  • the switching of the control unit 12 is preferably carried out manually, but can also be done electrically, hydraulically or pneumatically.
  • the control unit 12 Via a first and second supply line 22, 24, the control unit 12 is connected to a hydraulic cylinder 26, wherein the first supply line 22 leads into a first chamber 28 of the hydraulic cylinder 26 and the second supply line 24 into a second chamber 30 of the hydraulic cylinder 26.
  • a piston 29 separates the two chambers 28, 30 from each other.
  • the first chamber 28 of the hydraulic cylinder 26 represents the piston-bottom side or stroke-side chamber, whereas the second chamber 30 represents the piston rod side and the lower side chamber of the hydraulic cylinder.
  • the load holding device 32 includes a pressure and spring-controlled pressure relief valve 34, and a non-return valve 36 which opens to the hydraulic cylinder side and which is arranged via a bypass line 38 parallel to the pressure limiting valve 34.
  • a control pressure line 40 Via a control pressure line 40, a pressure connection is made by the pressure limiting valve 34 to the hydraulic cylinder side portion of the first supply line 22.
  • Via a further control pressure line 42 is a pressure connection from the pressure relief valve 34, which is held by a spring 43 in the closed position, given to a shuttle valve 44.
  • the shuttle valve 44 is connected on the output side to the control pressure line 42 and on the input side to a further control pressure line 45.
  • the control pressure line 45 connects the shuttle valve 44 with the second supply line 24.
  • a hydraulic line 46 connects the first supply line 22 to a hydraulic accumulator 48, wherein the not connected to the hydraulic accumulator 48 end 50 of the hydraulic line 46 between the load holding device 32 and the switching device 12 is arranged.
  • a switching valve 52 is arranged in the hydraulic line 46.
  • the switching valve 52 is an electrically switchable seat valve, which is held by a spring 54 in the closed position and can be brought via a solenoid 56 in an open position.
  • the switching valve 52 can also be formed hydraulically switchable.
  • the switching valve 52 seals in the closed position in the direction of the hydraulic accumulator 48.
  • the switching valve 52 may also be designed such that it seals leak-free in both directions. In the open position, a hydraulic flow in both directions is ensured to produce a suspension function between the hydraulic cylinder 26 and the hydraulic accumulator 48.
  • a further switching valve 60 is provided in the first supply line 22.
  • the switching valve 60 is held in its normal position by a spring 62 in an open position.
  • the second switching valve 60 can be brought into a closed position, wherein the switching valve in the direction of the control unit 12 closes leak-free.
  • the switching valve 60 it is also possible for the switching valve 60 to be electrically switchable.
  • the second supply line 24 is connected via a further line 66 to the hydraulic tank 20, wherein in the conduit 66, a switching valve 68 is arranged.
  • the switching valve 68 is preferably designed as a seat valve and is electrically switchable in an open position or in a closing direction of the hydraulic tank 20 position can be brought. It is also possible to form the switching valve 68 hydraulically or pneumatically switchable.
  • the hydraulic arrangement 10 is provided with a control pressure device 70.
  • the control pressure device 70 has a further conveying means 72, which is connected to the hydraulic tank 20. Furthermore, the Control pressure device 70, a control pressure valve 74, which is connected via a supply line 76 to the conveyor 72 and a further supply line 78 to the hydraulic tank 20.
  • the control pressure valve 74 can be switched in such a way that a control pressure line 80 can be connected either to the conveying means 72 or to the hydraulic tank 20.
  • the control pressure line 80 is connected on the input side to the shuttle valve 44. Furthermore, the control pressure line 80 is connected to the control pressure line 64 of the switching valve 60.
  • a sensor 82 which detects the position of the hydraulic cylinder 26.
  • the sensor 82 may be formed as a contact switch, which signals a specifiable position of the piston 29.
  • this sensor 82 may also be designed as a pressure sensor or pressure switch (see FIG. 1), the pressure sensor or pressure switch reproducing or switching a signal at a predeterminable pressure of the first chamber 28.
  • the control unit 12 is connected to a switch or sensor 84, which detects the position of the control unit 12 and outputs a control signal to an electronic control unit 86. Further, an activation switch 88 is provided, which is connected to the control unit 86. About the control unit 86 For example, the electrically switchable switching valves 52, 68 or the control pressure valve 74 can be switched.
  • the lift, lower, and neutral operating states for the hydraulic cylinder 26 when the suspension is not activated, i. the switching valves 52, 68 are in the closed position and the control pressure valve 74 is connected such that the control pressure line 80 is connected to the hydraulic tank 20 are controlled as follows via the control unit 12 in corresponding operating positions. As shown in Figures 1 to 6, the controller 12 is maintained in neutral, i. H. it is closed and there is no hydraulic flow. Via a control signal or, as shown in Figures 1 to 6, by manual operation, the control unit 12 is brought by means of the actuator 11 from the neutral position in the raising or lowering position.
  • the actuating device 11 can also be operated electrically, hydraulically or pneumatically.
  • the connection of the first supply line 22 to the conveyor 18 and the connection of the second supply line 24 to the hydraulic tank 20 is made.
  • the conveying means 18 connected to the hydraulic tank 20 fills the first chamber 28 of the hydraulic cylinder 26 via the first supply line 22 and via the switching valve 60 which is in the open position and via the check valve 36 of the load-holding device 32 (the pressure-limiting valve 34 of the load-holding device 32 is in the closed position)
  • the piston 29 moves in the direction of the second chamber 30 and presses the existing there oil through the second supply line 24 out in the hydraulic tank 20.
  • the controller 12 interrupts the connections to the conveyor 18 and the hydraulic tank 20, so that the pressure in the two chambers 28, 30 of the hydraulic cylinder 26 is maintained and the movement of the piston 29 is released.
  • the piston 29 stops.
  • the conveying means conveys oil into the second chamber 30 of the hydraulic cylinder 26, whereby the pressure building up in the second supply line 24 opens the pressure limiting valve 34 of the load holding device 32 via the control pressure line 45, the shuttle valve 44 and the control pressure line 42.
  • the piston 29 is moved in the direction of the first chamber 28, so that the oil flowing out of the first chamber 28 passes via the first supply line 22 and via the open pressure limiting valve 34 into the hydraulic tank 20.
  • the load holding device 32 thus ensures that the hydraulic cylinder 26 maintains its position in the neutral position or escape in the lifting and neutral position normally no oil from the pressurized first chamber 28 and that in the lowered position, the oil from the first chamber 28 via the open pressure relief valve 34th can drain away.
  • the load holding device 32 should be sensibly arranged as shown on the lifting side of the hydraulic cylinder 26, wherein the lifting side is the side of the hydraulic cylinder 26, in which a pressure for lifting a load is built up. In the embodiments illustrated in Figures 1 to 6, the lifting side is the first chamber 28 of the hydraulic cylinder 26, wherein by turning the hydraulic cylinder 26, the second chamber 30 could serve as a lifting side.
  • the control pressure line 40 is an overload protection, so that at high operating pressures in the first chamber 28 of the hydraulic cylinder 26, which may arise, for example, by excessive loads or by heating the hydraulic cylinder 26, a limit pressure is reached, which opens the pressure relief valve 34 to reduce pressure , In these normally deviating states, the pressure relief valve 34 can be opened via the control pressure line 40 in the lifting and neutral position.
  • the switching valve 60 is open in its normal position and allows a free flow in both directions.
  • the switching valve 60 is closed by a hydraulic control pressure, which moves the switching valve 60 in a switching position in which only a volume flow in the direction of the lifting cylinder 26 is allowed.
  • the switching valve 60 is so leak-proof that required standards for lowering a load can be met.
  • the shuttle valve 44 interconnects the control pressure lines 45, 80 coming from the control pressure valve 74 and the rod side of the lift cylinder 26 with the control pressure line 42 of the pressure relief valve 34 such that the pressure relief valve 34, which is part of the load holding device 32, can be controlled.
  • the control pressure valve 74 serves to direct the control pressure of the conveying means 72 to the pressure limiting valve 34 and to the switching valve 60, so that they are opened or closed.
  • the control pressure lines 42, 64, 80 are toward the hydraulic tank 20 relieved, so that the pressure relief valve 34 and the switching valve 60 are in the normal position (the pressure relief valve 34 is closed, the switching valve 60 is open).
  • the control pressure valve 74 is switched, hydraulic fluid flows via the control pressure lines 42, 64, 80 to the pressure limiting valve 34 and to the switching valve 60. In this case, the pressure limiting valve 34 is opened and the switching valve 60 is closed.
  • the hydraulic cylinder 26, the load holding device 32, the switching valve 52, the hydraulic accumulator 48 and the switching valve 60 and the connecting lines are preferably parts of a steel assembly.
  • This may be a valve block which is attached to the hydraulic cylinder 26 together with hydraulic accumulator 48 or an assembly of valves which are connected to steel pipes. This is necessary to meet certain standards that require protection against hose breakage.
  • Other parts of the hydraulic arrangement can also be integrated in said assemblies.
  • FIG. 1 With respect to the embodiment shown in Figure 1 is an activation of the suspension function by the with the Control unit 86 connected sensor 82, which detects a lowered position (when using a contact or position sensor) or a low-pressure operating state (when using a pressure sensor) of the hydraulic cylinder 26, enabled.
  • the activation switch 88 connected to the control unit 86 is actuated.
  • the control unit 86 actuates the switching valve 52 and brings this in an open position, through which the hydraulic accumulator 48 is connected to the supply line 22.
  • control pressure valve 74 is actuated, which releases a control pressure and via the control pressure lines 42, 80 in conjunction with the shuttle valve 44, the pressure relief valve 34 opens and via the control pressure lines 64, 80 brings the switching valve 60 in the leak-free closed position. Further, the switching valve 68 connected to the control unit 86 is simultaneously opened.
  • the actuation of the control pressure valve 74 creates a connection between the lifting side of the hydraulic cylinder 26 and the hydraulic accumulator 48, which is sealed leak-free to the hydraulic tank.
  • a sudden increase in pressure in the first chamber 28 of the hydraulic cylinder 26 (high speed) is not possible because the switching valve 52 can be traversed in its closed position in the direction of the hydraulic cylinder 26, so that on the part of the hydraulic accumulator 48 always a pressure equalization in the direction of the hydraulic cylinder 26 can take place ,
  • the hydraulic cylinder 26 can be raised or held over the operating positions already described, via the open connection (switching valve 52 is open) between the hydraulic cylinder 26 and hydraulic accumulator 48 a Hydraulic fluid exchange can take place and thus a suspension function is given.
  • the rod side or the second chamber 30 of the hydraulic cylinder 26 is connected to the hydraulic tank 20 (switching valve 68 is open) to allow a free swinging of the cylinder piston 29 and a cavitation effect in the chambers 28, 30 to prevent. If the suspension function is deactivated via the activation switch 88, the switching valves 52, 68 and the control pressure valve 74 are de-energized. The control pressure lines 42, 64, 80 are depressurized, whereby the pressure relief valve 34 are brought back into the closed position and the switching valve 60 in the open position.
  • the operating state sinks for the hydraulic cylinder 26 (retraction of the cylinder piston 29) is not possible with activated suspension function with the hydraulic arrangement shown in Figure 1, since the switching valve 60 is closed in the direction of the control unit 12.
  • the position of the control unit 12 is detected via the sensor 84. If the controller 12 in Lowered position, a control signal from the sensor 84 is automatically transmitted to the control unit 86 and the suspension function by switching the switching valve 52 and the control pressure valve 74 is deactivated. At the same time, the switching valve 68 is closed.
  • the hydraulic accumulator 48 empties via the open switching valve 60 and must be charged for a renewed activation of the suspension function.
  • the hydraulic cylinder 26 is brought to a fully lowered position, so that the pressure in the hydraulic cylinder 26 can build up together with the pressure in the hydraulic accumulator.
  • a re-activation of the suspension function can then be carried out after re-release by the sensor 82, since the hydraulic cylinder 26 has been brought into its fully lowered position.
  • the cylinder piston 29 With activated suspension function, the cylinder piston 29 can spring freely in the operating positions lifting and normal position. If it moves downwards through a shock transmitted to it, the oil from the first chamber 28 is forced into the hydraulic accumulator 48. The pressure building up in the hydraulic accumulator 48 causes the oil to flow back into the first chamber 28, so that the piston 29 moves upward again. This resilient movement is repeated, if necessary, until the shock has been completely compensated.
  • FIG 2 shows an alternative embodiment in which a deactivation of the suspension function for lowering the hydraulic cylinder 26 takes place only temporarily during the lowering state. Subsequently, without again driving into a release position detected by the sensor 82, the suspension function can be resumed.
  • the difference to the hydraulic arrangement shown in Figure 1 is that the switching valve 52 of the hydraulic accumulator 48 closes on both sides leak-free in its closed position, so that the hydraulic accumulator 48 can not empty in the closed position in the direction of the hydraulic tank 20.
  • a pressure equalization between hydraulic accumulator 48 and hydraulic cylinder is still ensured (which is given in the embodiment shown in Figure 1 via the switching valve 52 in the closed position in combination with the check valve 36) by a further provided with a check valve 90 line 92 is provided, the one Connects from the second chamber 28 of the hydraulic cylinder 26 to the hydraulic accumulator 48, wherein the check valve 90 closes in the direction of the hydraulic accumulator 48.
  • a pressure equalization can take place via the line 92
  • the hydraulic accumulator 48 can be emptied in a controlled manner via the pressure limiting valve 34, so that the pressure in the hydraulic accumulator 48 is equal to the pressure in the hydraulic cylinder 26 at each time of lowering.
  • the switching position of the control unit 12 is also detected via the sensor 84 here.
  • the activation of the switching valves 52, 68 and the control pressure valve 74 is effected by the control unit 86 for deactivating the suspension state for the duration of the operating state. If the control unit 12 is switched from the operating position sinks to another operating position, the switching valves 52, 68 and the control pressure valve 74 are switched again via the control unit 86 and the suspension function activated.
  • a sudden high-speed of the hydraulic cylinder 26 is not possible here as well, because of the check valve 90 in the hydraulic accumulator 48, the same pressure prevails as in the hydraulic cylinder 26. This function is important in the event that the load should have changed during the lowering of the boom ( simultaneously dumping and depositing a pallet).
  • a timing sequence of switching initiated by the control unit 86 may optionally be controlled by means of throttles, additional valves or electronic time delay elements.
  • FIG. 3 shows a further exemplary embodiment.
  • the switching valves 52, 60, 68 are designed as pressure-controlled switching valves 52, 60, 68 and are connected together via the control pressure valve 74.
  • time sequences can be controlled, for example via throttles (not shown).
  • the embodiment shown in Figure 3 further corresponds to the embodiment shown in Figure 1, wherein such a pressure-controlled arrangement and design of the switching valves 52, 60, 68 is also suitable for the embodiment shown in Figure 2.
  • FIG. 4 shows a further exemplary embodiment which essentially corresponds to the exemplary embodiment illustrated in FIG.
  • a pressure compensation device 94 is provided.
  • the pressure compensation device 94 comprises a line 96 which extends between the hydraulic accumulator 48 and the hydraulic cylinder 26 and is provided with a closing in the direction of the hydraulic cylinder 26 check valve 98.
  • a line 99 is provided, which extends between the hydraulic accumulator 48 and a switching valve 100 connected to the hydraulic tank 20 and is provided with a pressure compensator 102.
  • the pressure compensator 102 is actuated via pressure lines 104, 106 on the one hand by the pressure acting in the line 96 and on the other hand by the pressure acting in the line 99.
  • the pressure compensator 102 switches into a closed position or into an open position to the switching valve 100.
  • the switching valve 100 has a closing position in the direction of the hydraulic tank 20 and an opening position.
  • a sensor 82 for determining the position of the hydraulic cylinder 26 can be omitted here.
  • the hydraulic accumulator 48 is always charged here with at least the highest load pressure of the hydraulic cylinder 26 during a certain operating state. Here it is not necessary to lower the hydraulic cylinder 26 before the activation of the suspension state, but you can at any time activate the suspension state after a Pressure equalization between hydraulic accumulator 48 and hydraulic cylinder 26 has taken place.
  • Such a pressure equalization can be effected by switching the switching valve 100 by this is opened briefly. This can be done automatically by the control unit 86, for example, upon actuation of the activation switch 88 for the suspension state. However, a manual operation is also conceivable here.
  • the hydraulic arrangement illustrated in FIG. 4 is similar in function to the hydraulic arrangement of FIG. 1 described above.
  • FIG. This corresponds essentially to the embodiment and design of the embodiment shown in Figure 2, in which case the switching valve 52 has a leak-free in the direction of the control unit 12 closing position and the check valve 90 of the line 92 is arranged parallel to a arranged in the line 92 throttle 107.
  • no sensor 82 is necessary, which detects a position of the hydraulic cylinder, since by the described arrangement of check valve 90 and throttle 107 and the formation of switching valve 52 always a pressure equalization between hydraulic accumulator 48 and hydraulic cylinder 26 can take place.
  • the hydraulic cylinder 26 can not fall when activating the suspension function and can not rise or snap up. The suspension function is thus activated at any time, regardless of the position of the hydraulic cylinder 26.
  • FIG. 6 shows a further exemplary embodiment, which substantially equals the exemplary embodiment with regard to FIG. The difference is that the switching valve 52 is electrically driven.
  • the control valve 74 serves only to control the pressure relief valve 34.
  • the switching valves 52, 60, 68 and the control pressure valve 74 in particular, however, switching valve 60 and control pressure valve 74 are via the control unit 86th controlled and monitored. This is important to be able to ensure that the control pressure valve 74 closes the pressure limiting valve 34, should the switching valve 60 in the spring state, for example due to an electrical failure (cable break, coil burned, etc.) jump to its open position. If this does not happen, the hydraulic cylinder 26 would be able to descend uncontrolled in the suspension state.
  • Such electrical control of the Switching valve 60 is also conceivable for the other illustrated embodiments.
  • FIG. 7 shows a mobile telescopic loader 108 with a telescopically extendable boom 110 which is pivotably articulated to a frame 109 of the telescopic handler 108.
  • a hydraulic cylinder 26 for raising and lowering the boom 110 is arranged between the boom 110 and the frame 109.
  • the hydraulic cylinder 26 is pivoted to a first and a second bearing point 112, 114, wherein the piston rod side is articulated to the second bearing point 114 on the arm 110 and the piston bottom side to the first bearing point 112 on the frame 109.
  • the hydraulic tank 20, the conveyor 18 and the control unit 12 are positioned on or in a housing 115 and connected to each other via hydraulic lines 14, 16, 116. Furthermore, the supply lines 22, 24 between control unit 12 and hydraulic cylinder 26 in Fig. 7 can be seen.
  • the load holding device 32 and the switching valve 52 and the switching valve 60 are located in a common valve block directly on the hydraulic cylinder 26.
  • the switching valve 68 is positioned together with the control unit 12 in the housing 115.
  • the hydraulic accumulator 48 is preferably also arranged directly on the hydraulic cylinder 26, so that between the common valve block and the hydraulic accumulator 48, the hydraulic line 46 can be formed as a rigid connection that does not require a separate raw rupture protection device.
  • control or switching signals are generated, with which the switching valves 52, 60, 68 and the control pressure valve 74 in response to the sensors 82, 84 and the Activation switch 88 are controlled or switched.
  • An illustration of the last-mentioned components has been omitted in FIG. The arrangement of such components is prior art and can be made by a person skilled in a known manner. According to the switching positions described above, the hydraulic cylinder 26 can be actuated such that the boom 110 can be raised, held or lowered, wherein for the individual operating conditions, a suspension state is adjustable or activated, as the embodiments shown in Figures 1 to 6 are taken can.
  • hydraulic arrangement can also be applied to other vehicles, for example to wheel loaders or front loaders or to excavators or cranes, which have hydraulically actuated components that can be raised or lowered and where a suspension seems useful.

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EP05111001A 2004-11-23 2005-11-21 Arrangement hydraulique Withdrawn EP1659087A3 (fr)

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EP1914353A3 (fr) * 2006-10-19 2011-04-20 Hitachi Construction Machinery Co., Ltd. Engin de construction
EP2896839A1 (fr) * 2014-01-14 2015-07-22 Hydac System GmbH Dispositif de blocage et de pression
EP3771684A1 (fr) * 2019-07-30 2021-02-03 Linde Material Handling GmbH Chariot de manutention doté d'un dispositif de levage
EP3943440A1 (fr) * 2020-07-21 2022-01-26 Liebherr-Werk Nenzing GmbH Système hydraulique pour un support de chute en arrière et appareil de travail

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Publication number Priority date Publication date Assignee Title
EP1743981A1 (fr) 2005-07-13 2007-01-17 Deere & Company Agencement hydraulique
WO2008006730A1 (fr) * 2006-07-14 2008-01-17 Deere & Company Installation hydraulique
EA012366B1 (ru) * 2006-07-14 2009-10-30 Дир Энд Компани Гидравлическое устройство
WO2008013466A1 (fr) * 2006-07-24 2008-01-31 Sorin Dinu Procédé et dispositif de récupération de l'énergie générée par l'opération d'abaissement du bras
EP1914353A3 (fr) * 2006-10-19 2011-04-20 Hitachi Construction Machinery Co., Ltd. Engin de construction
US8204655B2 (en) 2006-10-19 2012-06-19 Hitachi Construction Machinery Co., Ltd. Construction machine
EP2896839A1 (fr) * 2014-01-14 2015-07-22 Hydac System GmbH Dispositif de blocage et de pression
EP3771684A1 (fr) * 2019-07-30 2021-02-03 Linde Material Handling GmbH Chariot de manutention doté d'un dispositif de levage
EP3943440A1 (fr) * 2020-07-21 2022-01-26 Liebherr-Werk Nenzing GmbH Système hydraulique pour un support de chute en arrière et appareil de travail
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DE102004056418A1 (de) 2006-05-24
EP1659087A3 (fr) 2012-05-30
US7530434B2 (en) 2009-05-12
US20060108185A1 (en) 2006-05-25
DE102004056418B4 (de) 2013-02-28

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