EP1743979B1 - Hydraulic arrangement - Google Patents

Hydraulic arrangement Download PDF

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Publication number
EP1743979B1
EP1743979B1 EP20060116997 EP06116997A EP1743979B1 EP 1743979 B1 EP1743979 B1 EP 1743979B1 EP 20060116997 EP20060116997 EP 20060116997 EP 06116997 A EP06116997 A EP 06116997A EP 1743979 B1 EP1743979 B1 EP 1743979B1
Authority
EP
European Patent Office
Prior art keywords
switching
hydraulic
valve
arrangement
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
EP20060116997
Other languages
German (de)
French (fr)
Other versions
EP1743979A1 (en
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
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Filing date
Publication date
Priority to DE200510033535 priority Critical patent/DE102005033535A1/en
Application filed by Deere and Co filed Critical Deere and Co
Publication of EP1743979A1 publication Critical patent/EP1743979A1/en
Application granted granted Critical
Publication of EP1743979B1 publication Critical patent/EP1743979B1/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003Systems with load-holding valves
    • EFIXED CONSTRUCTIONS
    • E02HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02FDREDGING; SOIL-SHIFTING
    • E02F3/00Dredgers; Soil-shifting machines
    • E02F3/04Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36Component parts
    • E02F3/3604Devices to connect tools to arms, booms or the like
    • E02F3/3609Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat
    • E02F3/3663Devices to connect tools to arms, booms or the like of the quick acting type, e.g. controlled from the operator seat hydraulically-operated
    • EFIXED CONSTRUCTIONS
    • E02HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02FDREDGING; SOIL-SHIFTING
    • E02F9/00Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20Drives; Control devices
    • E02F9/22Hydraulic or pneumatic drives
    • E02F9/226Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/30505Non-return valves, i.e. check valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/31Directional control characterised by the positions of the valve element
    • F15B2211/3138Directional control characterised by the positions of the valve element the positions being discrete
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/315Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/32Directional control characterised by the type of actuation
    • F15B2211/321Directional control characterised by the type of actuation mechanically
    • F15B2211/324Directional control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/40Flow control
    • F15B2211/455Control of flow in the feed line, i.e. meter-in control
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/50Pressure control
    • F15B2211/505Pressure control characterised by the type of pressure control means
    • F15B2211/50563Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/50Pressure control
    • F15B2211/515Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5158Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and an output member
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/50Pressure control
    • F15B2211/52Pressure control characterised by the type of actuation
    • F15B2211/528Pressure control characterised by the type of actuation actuated by fluid pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/50Pressure control
    • F15B2211/575Pilot pressure control
    • F15B2211/5753Pilot pressure control for closing a valve
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/70Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051Linear output members
    • F15B2211/7053Double-acting output members
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/70Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/72Output members, e.g. hydraulic motors or cylinders or control therefor having locking means

Description

  • The invention relates to a hydraulic arrangement for a tool locking a charger, comprising a first and a second chamber having hydraulic cylinder having a first position for unlocking and a second position for locking, a hydraulically connected to the first chamber first supply line, one with the second chamber hydraulically connected second supply line and a hydraulically connected to the first chamber switching valve. The switching valve has a first switching position and a second switching position, wherein the switching valve in the first switching position allows a hydraulic flow only in the direction of the first chamber and in the second switching position hydraulic flow both to the first chamber and out of the first chamber out allows, wherein the switching valve is controlled such that it assumes the first switching position when the hydraulic cylinder assumes its first position to prevent incorrect operation of the hydraulic cylinder, and wherein a control pressure arrangement is provided, with which the switching valve can be brought into its first switching position.
  • Hydraulic arrangements for locking work tools on loaders such. As telehandlers or front loaders are known. In this case, hydraulic cylinders are used as locking cylinder, so that the working tools can be hydraulically mounted on the tool carrier of the charger. The control of the locking cylinder on the tool carrier, which are used for example for attaching tools such as blades, for example, via manually operated 6/2 way valves with which the locking cylinder can be switched on and off. Such 6/2 way valves are arranged so that at the same time no other hydraulic functions can be operated on the tool. Only by switching the 6/2 way valve in its second switching position, the tool is controlled, but at the same time interrupted the hydraulic supply of the locking cylinder. An operator quickly notices that she has forgotten something when she wants to operate a hydraulic function on the tool and the 6/2 way valve has not been brought into its second switching position. In such a hydraulic arrangement, however, there is a risk that the locking of the locking cylinder is forgotten and switched to the second switching position for operating the tool. In this case, a tool, for example, when dumping a blade, suddenly drop, which represents a significant security risk. Furthermore, such 6/2 way valves are more expensive compared to simpler switching valves.
  • In the US 2004/0244575 A1 a hydraulic arrangement for a tool lock of a charger of the type mentioned is disclosed. The hydraulic arrangement comprises a hydraulic cylinder for locking or unlocking a tool. The unlocking of the tool is subject to a hydraulic safety function that should prevent unintentional unlocking.
  • Furthermore, it is also known to operate such a hydraulic arrangement instead of the manually operated 6/2 way valve with a ball valve. This ball valve must be closed by the operator after the locking cylinders have been extended for locking. It is not necessary to close the ball valve so that it will not work if the hydraulic control units are operated incorrectly accidentally comes to unlock the locking cylinder and thus a tool can suddenly come off the tool carrier and fall down. However, this is possible with open ball valves and represents a corresponding operating error potential. It also has the disadvantage that an operator can operate all other auxiliary hydraulic functions on the tool, even if the ball valve is not closed.
  • The object underlying the invention is seen to provide a hydraulic arrangement of the type mentioned by which with respect to the hydraulic cylinder, the risk of incorrect operation by the operator is minimized.
  • The object is achieved by the teaching of claim 1. Further advantageous embodiments and modifications of the invention will become apparent from the dependent claims.
  • According to the invention, a hydraulic arrangement of the type mentioned is designed such that the control pressure arrangement is in hydraulic communication with the second chamber.
  • The switching valve is automatically switched to its first switching position as soon as the hydraulic cylinder assumes its first position, so that it is ensured that no more hydraulic oil can escape from the first chamber of the hydraulic cylinder. As a result, a safety function is created, since the hydraulic cylinder can indeed be hydraulically brought to its second position, but he did not return hydraulically from its second position to the first position can be, without bringing the switching valve in its second switching position (in the first switching position of the switching valve only a hydraulic flow is allowed in the direction of the first chamber). An operator is therefore always forced to perform an additional activity on the hydraulic arrangement (namely to bring the switching valve in the second switching position), if he wants to bring the hydraulic cylinder hydraulically from its second position to its first position. This considerably reduces the risk of incorrect operation of the hydraulic arrangement or of the hydraulic cylinder. Preferably, a control pressure arrangement is provided, with which the switching valve can be brought into its first switching position. The switching valve is then hydraulically switchable from its second switching position to the first switching position. However, it is also conceivable that the control pressure arrangement is replaced by an electronic circuit. The control valve would then be designed as an electrically switchable valve and could be switched from its second switching position electrically switchable in the first switching position. According to the invention, the control pressure arrangement is in hydraulic communication with the second chamber. This ensures that, as soon as the hydraulic cylinder has moved to its first position, a sustained hydraulic supply of the hydraulic cylinder leads to an increase in pressure in the control pressure arrangement until a certain switching pressure is reached and the switching valve is hydraulically and automatically brought into its first switching position , This ensures that the switching of the switching valve is directly connected to the position of the hydraulic cylinder and thus the switching valve is automatically switched depending on the position of the hydraulic cylinder. In the case of an electronic circuit or control For the switching valve, a sensor or switch could be used, which detects the position of the hydraulic cylinder and generates a switching signal when reaching the first position.
  • The switching valve is preferably latched in its second position, so that the switching valve has taken a somewhat secure switching position when it is in the second position.
  • The switching valve is preferably placed manually in the second position, so that the operator must go to the switching valve to adjust the second switching position. Thus, incorrect operation is unlikely because the operator can bring the switching valve aware and not accidentally in the second switching position. Nevertheless, a remote control is conceivable, for example by an electric switch or by a hydraulic valve control, which moves the switching valve in its second switching position. Thus, the risk of misuse would still be relatively low, as the operator is then forced to actuate at least one activation switch to activate the remote control.
  • The control pressure arrangement is provided with an openable in the direction of the switching valve pressure relief valve, which can be controlled by a pressure prevailing in the second chamber. This ensures that a certain control pressure must be achieved before the control pressure line of the switching valve is supplied with a hydraulic control pressure.
  • The control pressure arrangement further comprises a check valve which can be opened in the direction of the first chamber, the check valve being in hydraulic communication with the second chamber parallel to the pressure relief valve. The control pressure built up in the control pressure line can be reduced in this way if the switching operation of the switching valve has been made.
  • Preferably, the control pressure arrangement has a means for pressure shut-off, in particular a screw plug, with which the control pressure for switching the switching valve is turned off. This allows an operator to lock the automatic control pressure arrangement for the switching valve or to deactivate the control pressure arrangement.
  • Preferably, the means for pressure shut-off between the pressure relief valve and the second supply line is arranged. This has the advantage that the pressure for the pressure relief valve can be set to a value at which it is ensured that this pressure is not already reached by friction of the hydraulic cylinder or the associated parts and thus accidentally the switching valve in its first Switch position is brought. In the event that the friction is too high and the switching valve is always switched back to its first switching position, the screw plug can help, since this is basically open, but can also be closed. Then, the switching valve can be arbitrarily adjusted and the hydraulic cylinder can be moved from its second to its first position without the switching valve is automatically pressed into its first switching position. However, this mode of operation should not be attempted, since there is a risk that the operator forgets to switch the switching valve by hand to its first switching position.
  • In an alternative embodiment of the invention, the means for pressure shut-off between the switching valve and the first supply line and between the means for pressure shut-off and the first supply line is in the direction of the first supply line opening Check valve arranged. This provides a further possibility for deactivating the automatic hydraulic pressure control of the switching valve. Here, the screw plug is permanently closed as a means for pressure limiting and is only opened for deactivation. If the screw plug is open, the oil can flow off via the non-return valve without pressure.
  • Preferably, the hydraulic arrangement is designed as a valve block, in particular as an end plate design. However, it is also conceivable to arrange the components required for the hydraulic arrangement according to the invention separately.
  • The design of the hydraulic arrangement as a valve block in the end plate design enables the valve block to have suitable connections for the connection of hydraulic quick couplers. Furthermore, such a valve block may also be provided with further connections, to which further electrically switchable valves, for example 6/2-way valves, can be flanged.
  • A hydraulic arrangement according to the invention is particularly suitable as a locking system for a working tool of a loader vehicle, with which a security compared to conventional locking systems with respect to operator errors is created.
  • Reference to the drawing, which shows an embodiment of the invention, the invention and further advantages and advantageous developments and refinements of the invention are described and explained in more detail below.
  • It shows:
  • Fig. 1
    a schematic circuit diagram of a first embodiment of a hydraulic arrangement according to the invention,
    Fig. 2
    a schematic circuit diagram of a second embodiment of a hydraulic arrangement according to the invention and
    Fig. 3
    a schematic circuit diagram according to the embodiment in FIG. 1 as a valve block design.
  • In FIG. 1 a hydraulic arrangement 10 is shown, which comprises a hydraulic cylinder 12, a first supply line 14, a second supply line 16, a switching valve 18 and a control pressure arrangement 20. The hydraulic cylinder may be connected to a mechanism, not shown, which serves for locking and unlocking a working tool on a tool carrier. The supply lines 14, 16 are connected in a known manner with a hydraulic supply device 22, not shown, which comprises a hydraulic tank, a hydraulic pump and a control unit for controlling the hydraulic fluid delivered by the hydraulic pump or for hydraulically actuating the hydraulic cylinder 12.
  • The hydraulic cylinder 12 has a first chamber 24 and a second chamber 26 and a piston 30 connected to a piston rod 28. In the illustrated embodiment, the piston-side chamber of the Hydraulic cylinder 12, the first chamber 24 and the rod-side chamber, the second chamber 26 represents. Here, the chambers 24, 26 of the hydraulic cylinder can of course be assigned in the reverse manner, the piston rod 28 and the piston 30. The first chamber 24 is hydraulically connected to the first supply line 14. The second chamber 26 is hydraulically connected to the second supply line 16. By actuating the hydraulic cylinder 12 or by extending and retracting the piston 30 and the piston rod 28, a mechanism for locking or unlocking a working tool (also not shown) connected to a tool carrier (not shown), for example a loader bucket or a loading fork, is actuated become.
  • The switching valve 18 is disposed in the first supply line 14. It is preferably designed as a valve slide and has a first switching position 32 and a second switching position 34 and is urged by a spring 36 in the first switching position. Further, the switching valve 18 has a first switching position 32 associated control pressure port 38 through which the switching valve 18 is hydraulically switchable in its first switching position 32. About a second switching position 34 associated manual actuator 40, the switching valve 18 can be brought into its second switching position 34. The actuating device 40 additionally has a latching device 42, with which the switching valve 18 can be latched into its second switching position 34 after manual actuation. The first switching position 32 is designed such that a hydraulic flow through the first supply line 14 is permitted only in the direction of the first chamber 24 of the hydraulic cylinder 12. In the opposite Direction closes the switching valve 18 in its first switching position 32 leak-tight. The second switching position 34 is designed such that a hydraulic flow through the first supply line 14 is permitted in both directions, ie both out to the first chamber 24 of the hydraulic cylinder 12 and out of the first chamber 24 of the hydraulic cylinder 12 out.
  • The control pressure arrangement 20 has a first and a second hydraulic line 50, 52, wherein the first hydraulic line 50 represents a control pressure line from the second supply line 16 to the control pressure port 38 of the switching valve 18. The second hydraulic line 52 represents a bypass line extending between the first hydraulic line 50 and the second supply line 16 and having a common connection point 54 with the first hydraulic line 50. In the first hydraulic line 50, a pressure relief valve 56 is arranged between the connection point 54 and the second supply line 16, which is biased by a spring 58 in a closed position and can be controlled via a control pressure line 60. In the second hydraulic line 52 a in the direction of the second supply line 16 opening check valve 62 is arranged. Furthermore, between the overpressure valve 56 and the second supply line 16, a means 64 designed for example as a screw plug is arranged for pressure shutoff.
  • For those in the FIGS. 1 to 3 illustrated embodiments, it is assumed that an extension of the piston rod 28 with a locking position of the hydraulic cylinder 12 for a working tool on a Tool carrier is connected or retraction is connected to an unlocked position. Of course, by reversing the arrangement of the hydraulic cylinder and a corresponding arrangement of the locking mechanism, not shown, a reverse operation can be achieved.
  • According to the in FIG. 1 The second chamber 26 of the hydraulic cylinder 12 is hydraulically pressurized to retract the hydraulic cylinder 12 and the piston rod 28 and to bring the hydraulic cylinder 12 in a first position, an unlocking position. Accordingly, the first chamber 24 is hydraulically pressurized to extend the hydraulic cylinder 12 and the piston rod 28 and bring the hydraulic cylinder 12 in a second position, a locking position.
  • Starting from an unlocking position of the hydraulic cylinder 12, the first supply line 14 is pressurized via the hydraulic supply device 22 with hydraulic fluid. The switching valve 18 is in its first switching position 32, ie it is a hydraulic flow only in the direction of the first chamber 24 approved. The first chamber 24 is filled with hydraulic oil and the hydraulic cylinder is moved to its second position or into the locking position. Due to the fact that the switching valve 18 in its first switching position 32 does not permit any hydraulic flow out of the first chamber 24, the hydraulic cylinder 12 remains in its locking position, even if the second supply line 16 or the second chamber 26 would be pressurized with hydraulic fluid. Only by Switching the switching valve 18 in its second switching position 34, a drainage of the hydraulic fluid from the first chamber 24 is allowed. For this purpose, the switching valve 18 must first be manually operated by an operator, which then engages in its second switching position 34. Only then can be pressurized by pressurizing the second supply line, which is carried out by appropriate control of the supply device 22, the second chamber with hydraulic fluid. Since in the second switching position 34 of the switching valve 18, a hydraulic flow in both directions is allowed, the hydraulic fluid can flow out of the first chamber 24, so that the hydraulic cylinder 12 is moved to its first position or in the unlocked position. As soon as the hydraulic cylinder 12 assumes its first position, the pressure in the second chamber 26 or in the second supply line 16 and thus also in the first hydraulic line 50 increases. The increase in pressure causes the pressure relief valve 56 is opened via the control pressure line 60 and the switching valve 18 is acted upon by a control pressure, which moves it back into its first switching position 32. Via the check valve 62, the established control pressure can relax or the hydraulic fluid can flow off via the second supply line 16 when the hydraulic pressure in the second supply line 16 has dropped. The hydraulic cylinder 12 can now be extended again in a further cycle and brought into the locking position. As already described above, it can then only retracted again, or be brought into the unlocked position when the switching valve 18 is previously brought by the operator into its second switching position 34. This is in contrast to the usual functions of locking devices on loader vehicles or on Tool holders, increased security against incorrect operation of the locking device, as an operator can not inadvertently move the hydraulic cylinder 12 from its locking position to its unlocked position. For this purpose, a deliberate and desired action of the operator must first be made, namely the switching of the switching valve 18 in its second switching position 34, since after each retraction of the hydraulic cylinder 12, the switching valve 18 is automatically moved by the control pressure assembly 20 in the first switching position 32.
  • The pressure on the pressure relief valve 56 can be switched off so that it is ensured that a control pressure is not already achieved by friction of the hydraulic cylinder 12 and the associated locking mechanism or components and so accidentally the switching valve 18 is brought into its first switching position 32. In the event that the friction is too high and the switching valve 18 is repeatedly switched to its first switching position, the screw 64 can help, since this is basically open, but can also be closed. Then, the switching valve 18 can be adjusted as desired and the hydraulic cylinder 12 are moved from its second to its first position without the switching valve 18 is automatically pressed into its first switching position 32.
  • In principle, it is conceivable that by means of the control pressure at the switching valve 18, not the whole designed as a valve spool switching valve 18 is moved, but only a small plunger, for example, a the first switching position 32 performing check valve imprints to provide a switching position corresponding to the second switching position 34 of the switching valve 18. Numerous constructional variations are conceivable here, whereby in principle the manual opening and hydraulic closing of the leak-tight switching valve is achieved.
  • It is also conceivable that not all of the valve spool designed as a switching valve 18 is actuated, but only the latching device 42 is unlatched by hydraulic pressure, so that the switching valve is brought by means of a return spring from the second switching position 34 back into its first switching position 32.
  • In another in FIG. 2 illustrated embodiment, a third hydraulic line 66 is provided, which extends from the first hydraulic line 50 to the first supply line 14. For this purpose, a further connection point 67 is provided between the connection point 54 and the switching valve 18, which connects the third hydraulic line 66 with the first hydraulic line 50. Unlike the in FIG. 1 illustrated embodiment, the screw plug is arranged as a means 64 for pressure shut-off in the third hydraulic line 66. In addition, a check valve 68 opening in the direction of the first supply line 14 is provided between the means 66 for switching off the pressure and the first supply line 14.
    The functionality essentially corresponds to that in FIG. 1 described operation and is merely another possibility, with the above-described problem of pressure shutdown at high frictional resistance on the hydraulic cylinder 12 or on the locking device can be corrected. Normally, the in FIG. 2 closed plug shown. If the closure screw 64 is opened, then the hydraulic fluid that supplies the control pressure for the switching valve can flow off via the check valve 68. As a result, the control pressure device can be quasi deactivated or operated virtually without effect, so that no automatic pressure control for the switching of the switching valve 18 in the first switching position 32 takes place.
  • Preferably, the hydraulic arrangement according to the invention is formed as a valve block 70, as in FIG. 3 is shown schematically. The implementation of the hydraulic arrangement as a valve block 70 in the end plate design allows the valve block 70 to have suitable ports for the connection of hydraulic quick couplers 72. The hydraulic arrangement can be made in a particularly compressed and space-saving way. The valve block is arranged as a contiguous building block between the hydraulic cylinder 12 and the quick couplers 72. This in FIG. 3 illustrated concept of the valve block construction is both for the in FIG. 1 as well as for in FIG. 2 illustrated embodiment suitable.
  • Although the invention has been described with reference to two embodiments, many different alternatives, modifications, and variations that are within the scope of the present invention will become apparent to those skilled in the art in light of the foregoing description and the drawings.

Claims (10)

  1. Hydraulic arrangement for a tool-locking mechanism of a loader, comprising a hydraulic cylinder (12) having a first and a second chamber (24, 26), which hydraulic cylinder has a first position for unlocking and a second position for locking; a first supply line (14) hydraulically connected to the first chamber (24); a second supply line (16) hydraulically connected to the second chamber (26); and a switching valve (18) hydraulically connected to the first chamber (24), wherein the switching valve (18) has a first switching position (32) and a second switching position (34), wherein in the first switching position (32) the switching valve (18) allows a hydraulic flow only in the direction of the first chamber (24) and in the second switching position (34) allows a hydraulic flow both towards the first chamber (24) and out of the first chamber (24), wherein the switching valve (18) can be activated in such a way that it assumes the first switching position (32) when the hydraulic cylinder (12) assumes its first position so as to prevent faulty operation of the hydraulic cylinder (12), and wherein a control pressure arrangement (20) is provided by means of which the switching valve (18) can be brought into its first switching position (32), characterized in that the control pressure arrangement (20) is hydraulically connected to the second chamber (26).
  2. Hydraulic arrangement according to Claim 1, characterized in that the switching valve (18) can be latched in its second switching position (34).
  3. Hydraulic arrangement according to Claim 1 or 2, characterized in that the switching valve (18) can be brought manually into its second switching position (34).
  4. Hydraulic arrangement according to one of Claims 1 to 3, characterized in that the control pressure arrangement (20) comprises a pressure-relief valve (56) which can be opened in the direction of the switching valve (18) and which can be actuated by a pressure prevailing in the second chamber (26).
  5. Hydraulic arrangement according to one of Claims 1 to 4, characterized in that the control pressure arrangement (20) comprises a non-return valve (62) which can be opened in the direction of the second supply line (16) and which is hydraulically connected to the second chamber (26) parallel to the pressure-relief valve (56).
  6. Hydraulic arrangement according to one of Claims 1 to 5, characterized in that the control pressure arrangement (20) comprises a means (64) for disconnecting the pressure, in particular a closure screw, by means of which the control pressure can be cut off in order to switch the switching valve (18).
  7. Hydraulic arrangement according to Claim 6, characterized in that the means (64) for disconnecting the pressure is arranged between the pressure-relief valve (56) and the second supply line (16).
  8. Hydraulic arrangement according to Claim 6, characterized in that the means (64) for disconnecting the pressure is arranged between the switching valve (18) and the first supply line (14), and a non-return valve (68) which opens in the direction of the first supply line (14) is arranged between the means (64) for disconnecting the pressure and the first supply line (14).
  9. Hydraulic arrangement according to one of the preceding claims, characterized in that it is configured as a valve block (70), in particular as an end plate design.
  10. Hydraulic arrangement according to Claim 9, characterized in that the valve block (70) comprises connections suitable for connecting hydraulic quick couplings (72).
EP20060116997 2005-07-14 2006-07-11 Hydraulic arrangement Expired - Fee Related EP1743979B1 (en)

Priority Applications (1)

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DE200510033535 DE102005033535A1 (en) 2005-07-14 2005-07-14 Hydraulic arrangement

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EP1743979B1 true EP1743979B1 (en) 2011-08-10

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US9617129B2 (en) * 2010-03-16 2017-04-11 Brookefield Hunter, Inc. Hydraulic pumping cylinder and method of pumping hydraulic fluid
US20140158962A1 (en) * 2011-03-16 2014-06-12 Brookfield Hunter, Inc. Hydraulic pumping cylinder and method of pumping hydraulic fluid
US8974137B2 (en) 2011-12-22 2015-03-10 Caterpillar Inc. Quick coupler
US8684623B2 (en) 2012-05-30 2014-04-01 Caterpillar Inc. Tool coupler having anti-release mechanism
US8869437B2 (en) 2012-05-30 2014-10-28 Caterpillar Inc. Quick coupler
US9217235B2 (en) 2012-05-30 2015-12-22 Caterpillar Inc. Tool coupler system having multiple pressure sources
DE102012107567B4 (en) * 2012-08-17 2015-03-19 Lehnhoff Hartstahl Gmbh & Co. Kg Quick coupler, method for operating a quick coupler and quick-change device
KR101471288B1 (en) * 2013-05-06 2014-12-09 현대중공업 주식회사 Swing device of excavator with anti-sliding device
US9228314B2 (en) 2013-05-08 2016-01-05 Caterpillar Inc. Quick coupler hydraulic control system
DE102018115249A1 (en) * 2018-06-25 2020-01-02 Lehnhoff Hartstahl Gmbh Quick changer and quick change device with a quick changer

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DE102005033535A1 (en) 2007-01-18
US7430955B2 (en) 2008-10-07
EP1743979A1 (en) 2007-01-17
US20070022750A1 (en) 2007-02-01

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