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
  • 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
  • F15B11/0406—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed during starting or stopping
• • 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
  • F15B2211/3051—Cross-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
  • F15B2211/3052—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
  • F15B2211/30—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
  • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
  • F15B2211/3127—Floating position connecting the working ports and 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
  • F15B2211/30—Directional control
  • F15B2211/32—Directional control characterised by the type of actuation
  • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
• • 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
  • F15B2211/40—Flow control
  • F15B2211/405—Flow control characterised by the type of flow control means or valve
  • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
• • 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
  • F15B2211/40—Flow control
  • F15B2211/41—Flow control characterised by the positions of the valve element
  • F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
  • F15B2211/40—Flow control
  • F15B2211/42—Flow control characterised by the type of actuation
  • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid 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
  • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
  • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
  • F15B2211/7051—Linear output members
  • F15B2211/7053—Double-acting output members
• • 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
  • F15B2211/85—Control during special operating conditions
  • F15B2211/851—Control during special operating conditions during starting

Definitions

• the invention relates to an actuating device for controlling at least one hydraulic consumer, such as a working cylinder, by means of a fluid supply stream.
• actuators are known in a variety of different embodiments and freely available on the market.
• the known actuators are used to control work machines, such as excavators, tractors, harvesters and cranes, but are also used for hydraulic lifts, forklifts, elevators, etc. and for various types of hydraulically operated machines, including machine tools, plastic injection molding machines, etc.
• a variety of other applications such as power plant technology, off-shore technology, wind farms, aerospace engineering, also employ such actuators to initiate motion and work operations.
• actuators are regularly required as hydraulic consumers, for example in the form of pumps, hydraulic motors or working cylinders. The enumeration is only an example and not exhaustive.
• the invention has the object to further improve the known solutions to the effect that the disadvantages described above do not occur, in particular improved ease of use and Ergonomiesn account is taken.
• a related object solves an actuator with the features of claim 1 in its entirety. Characterized in that according to the characterizing part of claim 1 by means of a drive unit, the fluid supply current is controlled for the consumer so that a muted operation is achieved with a gentle starting behavior, it comes basically for the hydraulic consumer to gentle accelerations, with respect to the steady Speed behavior of the operator are perceived as pleasant and any hydraulic or hydraulic actuators connected to the mechanical or hydraulic actuators are protected in the context of the respective work and actuation process and the entire hydraulic system relieved of undesired pressure surges.
• the actuating device according to the invention with drive unit for the fluid supply flow that when moving a control cabin of an excavator or a crane in each displacement position, the acceleration for the cabin is smooth, which in addition to an increased ease of use also contributes to operator safety.
• the drive unit used can be chosen so that existing machine complexes can be retrofitted and that the actuator according to the invention with the oil purities on the ground comes home, even if they should be of poor quality. Since the drive unit represents a substantially pure hydraulic solution, no changes to the electronics or electrical system are necessary in a retrofit of existing units, which helps to save costs. Overall, the actuator according to the invention can be designed more cost-effective than the known use of a variety of cost-intensive proportional directional spool valves with expensive control electronics used.
• FIG. 4 shows a longitudinal section for a usable for the hydraulic actuator proportional valve as a throttle.
• the actuating device shown in the manner of a hydraulic circuit diagram according to Figure 1 is used to control at least one hydraulic consumer 10 in the form of a hydraulic differential cylinder.
• a pertinent differential cylinder could also occur a Gleichgangzylinder or a hydraulic motor and comparable consumers who want to help to a smooth starting behavior.
• the hydraulic consumer 10 in the form of the working cylinder has a piston rod unit 12 which separates two hydraulic working spaces 14,16 from each other. The construction of this working cylinder or actuators is common, so that will not be discussed in more detail here at this point.
• the working space 14 also called piston working space, is connected via a connection A with the actual hydraulic circuit and the working space 16, which is also called bar working space, with the corresponding junction B.
• the terminals S1 and S2 shown in the upper part of the hydraulic circuit seen serve the connection of corresponding sensors, for example for pressure value detection in the corresponding hydraulic lines, each open at the connection points A, B to the outside, wherein the actuating device is preferably designed in the manner of a hydraulic modular control block.
• the actuating device in addition to the Nutzanêtn A, B nor a hydraulic supply port P and a drain T, which preferably opens at ambient pressure in a corresponding supply tank.
• the hydraulic supply at port P can be done via a corresponding hydraulic pump.
• the numbers 1, 2, 3 and 4 appear in the hydraulic circuit diagram shown in FIG. 1, they each indicate the hydraulic inputs and outputs for the respective hydraulic valve or other control components. te. If reference is made in the following to certain inputs and outputs of a pertinent hydraulic component, the cited paragraphs will be consulted for the more detailed determination.
• an adjustable throttle 18 is provided below the useful connections A, B in a corresponding arrangement and a non-return valve 20 opens in the auxiliary branch in the direction of the utility connections Supply line for the Nutzan say A and B two mutually releasable check valves 22 connected.
• the pertinent hydraulic supply structure for the Nutzan say A, B is common, so that will not be discussed in more detail here at this point.
• a proportional valve 24 is connected, which forms a kind of throttle or throttle valve.
• Proportional valves are continuously adjustable pressure, flow and directional valves that can convert a variable input signal into a proportional hydraulic output signal.
• a diaphragm 26 is connected, which throttles the fluid supply flow coming from the supply pump so far.
• the proportional valve 24 has two control inputs 28,30, wherein at the control input 28, the fluid pressure at the point 1 of the proportional valve 24 is present and at the control input 30 of the set pressure of a compression spring 32 (see FIG.
• the working space of the compression spring 32 is connected via the terminal 4 of the proportional valve 24 and thus via a leakage oil connection 34 with the tank T.
• a diaphragm 36 is connected in the secondary branch between the connection points 2 and 3 of the proportional valve 24, in turn.
• a slide valve 38 which is in the manner of a 4/3-way Slide valve is formed with a further connection point 1, which is connected to the tank connection T and the leakage oil connection 34.
• the pertinent slide valve 38 is spring-centered on both sides held in the initial position shown and can be via appropriate actuation or switching solenoids in a known manner.
• the output 4 of the spool valve 38 opens in the direction of the Fig.1 seen on the right side in the line for the Nutzanschluß B, via the input 1 of the pilot operated check valve 22. On the left opposite terminal side opens the output 4 of the spool valve 38th on the input side 1 of a shuttle valve 40 of known type.
• the further input 3 of the change venti Is 40 opens on the input side 1 of the left-handed check valve 22. Furthermore, the further input 3 of the shuttle valve 40 opens to the other output 2 of the slide valve 38.
• the two check valves 22 open the control lines on the input side 3 of the check valves 22 in each case in the opposite supply line for the Nutzan bend A, B.
• the output 2 of the shuttle valve 40 in turn opens via an aperture 42 to the input side 1 with the control input 28, in turn, another aperture 44 is connected.
• a pressure relief valve 46 is connected, which is formed in the present case as a spring-loaded check valve with opening direction in the direction of the tank port T.
• the drive unit designated as a whole by 48 consists essentially of the pressure relief valve 46 and of the orifices 42 and 44.
• the pertinent control unit 48 controls the fluid supply flow for the consumer 10 in such a way that a damped actuation with a gentle starting behavior for the hydraulic consumer 10 in the form of the working cylinder is achieved.
• the system pressure prevailing in the region of the shuttle valve 40 which supplies the useful ports A, B, can assume a wide range of pressure values within a certain fluctuation range and depending on the load acting in the system on the hydraulic cylinder 10, different volume flows occur, in particular with respect to the diaphragm 42 between the shuttle valve 40 and pressure relief valve 46.
• the slide valve 38 To generate the damped travel movement, the slide valve 38 must first be actuated, which can take place via a suitable actuation or control device triggered by an operator.
• the pressure relief valve 46 and the acting spring force on the compression spring 32 on the oppositely acting control input side 30 is taking into account the geometry of the piston 50 of the proportional valve 24 (see Fig.4) determines the opening characteristic for the throttle 24 and thus the damping effect for the entire system.
• this also increases the fluid supply flow for the hydraulic consumer 10, the opening behavior of the throttle in the form of the proportional valve 24 being independent of the load pressure at the consumer 10 due to the pressure limiting valve 46. Due to such a steady increase of the fluid flow to the hydraulic consumer 10, this drives smoothly and continuously until it reaches the maximum speed.
• the displaced in the rod working chamber 16 fluid in the pertinent Ausfahrbewe- movement of the piston rod unit 12 is pushed through the Nutzanschluß B and the terminal 4 of the spool valve 38 in the direction of the tank port T in the tank.
• the closing element of the shuttle valve 40 is brought into the upper position, which points in the direction of the input 3 of the shuttle valve 40, so that the input 1 to the output 2 of the shuttle valve 40 is fluidly connected and in turn via the proportional valve 24 in a throttled manner and thus gently the retraction movement of the piston rod unit 12 can take place.
• the aperture 42 has the same aperture diameter as the aperture 36 and that the further aperture 44 has a smaller aperture diameter than the aperture 42 and 36, wherein the aperture 26 arranged on the pump inlet side should have the smallest aperture diameter.
• the shuttle valve 40 operates in the manner of a tapping point, wherein a pertinent tapping point (not shown) via other hydraulic means would be realized, but this is associated with a correspondingly increased circuit complexity.
• the combination of an initial throttling via the proportional valve 24 with the inlet panel 36 ensures that pressurized fluid is present on the inlet side of the actuating or sliding valve 38 even in the non-switched state for the gentle starting process of the consumer.
• the indicated hydraulic switching unit can basically be used for each hydraulic consumer, even if the requirements for the initial volume flow are different. If a modified solution according to the illustration according to FIG. 3 is used in which the orifice 36 has been omitted, a changed proportional valve 24 with a calculated throttled basic supply would basically have to be used each time changing requirements for the initial volumetric flow occur , which would lead to increased costs for the hydraulic circuit.
• the proportional valve may also be closed in the switched position shown, in which case the entire adaptation via the orifice 36 must take place, which may also be the adaptation possibilities for the hydraulic circuit limited.
• the combination of initial throttling shown in FIG. 1 via the proportional valve 24 with inserted diaphragm 36 with permanent diaphragm cross-section makes sense, in particular from a cost-technical point of view, if the proportional valve 24 is designed for the smallest occurring volume flow and the larger volume flows is realized by the parallel connection of the diaphragm 36 to the proportional valve 24. Also results from the pertinent arrangement, an increased dynamic behavior in the soft damped startup of the hydraulic load 10. If the embodiments of Figures 2 and 3 compared to the solution according to Fig.1 are changed, only the essential changes have been explained and otherwise, the same reference numerals are used for the same components, as indicated in Fig. 1.
• FIG. 4 The constructive solution of the proportional valve 24 is shown in Figure 4.
• a further housing part 54 is screwed in on the upper side of the housing 52, essentially accommodating the compression spring 32, which with its one free end adjoins the inside of the other Housing part 54 is supported and at its other end to the displacement or control piston 50, which performs the throttling shown in Figure 1 between the terminals 2 and 3 of the proportional valve 24.
• the piston 50 has in each case to assume a basic position, in which there is still a minimum of throttling
• the piston 50 would then have to completely block the pertinent fluid path, so that the compensation can take place via the diaphragm 36.
• the piston 50 is equipped with a diameter-reduced control or annular groove 60 between two piston parts 56, 58 and the pressure prevailing at the control input 1 or 28 relative to the constant volume flow is then permanently at the bottom of the piston part 58.
• the spring chamber above the piston 50 opens into the leakage oil connection 34, which opens out to the tank side T.
• the actuating device according to the invention is preferably used there in which operating cabins of excavators or cranes have to move several meters forwards or upwards; Adjustment movements of the cabin, as they are necessary to make a timely unloading of ships od. Like. To make, where the operator needs an extended field of view. Thanks to the smooth start-up and stop movements with linear velocity and acceleration behavior, the unpleasant rocking movements of the cabin, which otherwise occur, have been met, which, in addition to increasing operating convenience, also meets increased safety requirements.
• the proportional valve 24 is designed in the manner of a continuous valve.
• the proportional valve 24 can be used for poor oil cleanliness classes, which otherwise make the use of conventional proportional valves impossible, provided that they are provided with electrically actuated switching or actuating magnet. So far as in the present application of a proportional valve is mentioned, this means a continuous valve without the use of a switching or actuating magnet. Furthermore, all throttles and / or diaphragms used can be protected by sieves against contamination.

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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)
• Operation Control Of Excavators (AREA)

Applications Claiming Priority (2)

Publications (2)

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ID=38606463

Family Applications (1)

Country Status (4)

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Family Cites Families (7)

• 2006
  • 2006-08-10 DE DE102006037631A patent/DE102006037631A1/de not_active Withdrawn
• 2007
  • 2007-07-12 EP EP07786011A patent/EP2049802B1/fr not_active Not-in-force
  • 2007-07-12 WO PCT/EP2007/006179 patent/WO2008017359A1/fr not_active Ceased
  • 2007-07-12 AT AT07786011T patent/ATE523698T1/de active

Non-Patent Citations (1)

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