EP2171289A1 - Dispositif de commande pour au moins deux commandes hydrauliques - Google Patents

Dispositif de commande pour au moins deux commandes hydrauliques

Info

Publication number
EP2171289A1
EP2171289A1 EP08772899A EP08772899A EP2171289A1 EP 2171289 A1 EP2171289 A1 EP 2171289A1 EP 08772899 A EP08772899 A EP 08772899A EP 08772899 A EP08772899 A EP 08772899A EP 2171289 A1 EP2171289 A1 EP 2171289A1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
valve
valves
throttle
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Withdrawn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
EP08772899A
Other languages
German (de)
English (en)
Inventor
Franz Peter Salz
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.)
Bucher Hydraulics AG
Original Assignee
Bucher Hydraulics AG
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 Bucher Hydraulics AG filed Critical Bucher Hydraulics AG
Publication of EP2171289A1 publication Critical patent/EP2171289A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0433—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being pressure control valves
    • 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
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • 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
    • E02F9/2296—Systems with a variable displacement pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/166—Controlling a pilot pressure in response to the load, i.e. supply to at least one user is regulated by adjusting either the system pilot pressure or one or more of the individual pilot command pressures
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional 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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in control
    • 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
    • F15B2211/355—Pilot pressure control
    • 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
    • F15B2211/465—Flow control with pressure compensation
    • 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
    • F15B2211/6052—Load sensing circuits having valve means between output member and the load sensing circuit using 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/67—Methods for controlling pilot 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
    • F15B2211/70—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
    • F15B2211/70—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
    • F15B2211/7058—Rotary 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member

Definitions

  • Control device for at least two hydraulic drives
  • the invention relates to a control device for at least two hydraulic drives according to the preamble of claim 1.
  • Such control devices are suitable for example for controlling the hydraulic drives of a working device with a plurality of functions.
  • a working device may for example be a mobile crane with a telescopic arm, which is extendable, adjustable in height and rotatable.
  • a hydraulic drive is provided, so one for extending and retracting the telescopic arm, one for the adjustment of the inclination of the boom and one for rotating the boom.
  • a control device of this type is known in which in the event of the occurrence of an undersupply, a separate external pressure control valve is provided, by means of which the control pressure for the drives associated with the proportional valves is reduced.
  • the control pressure for the pilot control devices of the drives is reduced by means of this additional external pressure regulating valve and by means of the resulting Hubverring réelle to the drives associated directional control valves achieved a reduction in volume at all consumers. This means that all drives run slower.
  • This solution also requires an additional external servo cylinder.
  • control device for two hydraulic drive units is shown. Each of these units is assigned its own pump, so that the aforementioned problem of undersupply of a consumer can not occur. Nevertheless, this control device includes means for reducing a control pressure. However, this serves to reduce the speed of a consumer supplied by another, for example, a second pump.
  • the invention has for its object to provide a control valve block consisting of successive control valve units, each drive to be controlled is associated with such a control valve unit, wherein the individual control valve units are such that there are no other external components to prevent the undesirable effects of undersupply requirement. This ensures that, depending on the number of drives to be controlled, ie two, three or more, a corresponding number of control valve units can be strung together, but that no additional units to prevent the adverse effect of a shortage must be mounted.
  • FIG. 3 is a diagram of a pressure divider
  • Fig. 4 is a diagram with a circuit supplement
  • Fig. 5 is a diagram of a pressure divider with the circuit supplement.
  • FIG. 1 shows consumers 1, namely a first consumer 1.1 and a second consumer 1.2, which are controllable by a control device 2.
  • the control device 2 consists of individual control blocks 3, namely a first control block 3.1, which is associated with the consumer 1.1, and a second control block 3.2, which is associated with the consumer 1.2. If further consumers 1 are to be controlled, then the control device 2 additionally contains further control blocks 3, which is not shown in FIG.
  • the consumer 1.1 for example, a double-acting drive cylinder, the consumer 1.2 a hydraulic motor, which is indicated in Fig. 1 by corresponding symbols.
  • the consumers 1 are supplied from a pump 4 with pressure medium, for example hydraulic oil.
  • the pump 4 is a variable displacement pump with a flow regulator, which is shown symbolically. As in the prior art, a group of pumps 4 may be present instead of a single pump 4.
  • the pump 4 sucks the pressure medium from a tank 5 and supplies the pressure medium through a pump line 6 - A - the control device 2. From the control device 2 performs a tank line 7, the recirculated from the consumers 1 pressure medium in the tank 5 from.
  • Reference numeral 8 denotes a load pressure line which serves to control the pump 4. Shown is also a control oil return line 9, which is guided in the tank 5.
  • the control blocks 3.1 and 3.2 are constructed completely the same.
  • the control block 3.1 has a directional control valve 11.1, which controls the flow of pressure medium to and from the consumer 1.1 in a known manner.
  • the directional control valve 11.1 erfmdungshunt a pressure compensator 12.1 is connected upstream, although this has the disadvantage described in the introduction. According to the invention, this disadvantage is eliminated by a further measure according to the invention, which will be described below.
  • the directional control valve 11.1 is hydraulically controlled by means of a first proportional pressure reducing valve 13.1 and a second proportional pressure reducing valve 14.1.
  • the proportional pressure reducing valves 13.1 and 14.1 have electromagnetic drives, as shown symbolically. They are actuated by actuators, not shown, with the help of which the operator controls the corresponding drive 1.1.
  • Proportional pressure reducing valves 13.1 and 14.1 are thus pilot valves for the directional control valve 11.1. According to the invention, however, between the proportional pressure reducing valves 13.1 and 14.1 and the hydraulic control inputs of the directional control valve 11.1, a hydraulically controlled 2/2-way proportional valve 15.1 is connected, which forms a pressure divider together with throttle points.
  • a change valve 16.1 This communicates with the two load pressure connections of the directional control valve 11.1 and supplies the higher of the two load pressure values to a load pressure signaling line 17.1 which acts on a check valve 18.1 whose second connection is located on the load pressure line 8.
  • the second control block 3.2 shown to the right of the control block 3.1 is constructed exactly the same. It therefore contains the same elements, but here they are distinguished by the suffix .2 instead of .1.
  • a third control block and possibly also other control blocks can be present, which would each connect to the right of the control block 3.2, if they are present. In any case, passing through the individual control blocks 3 lines, namely the pump line 6, the tank line 7, the load pressure line 8 and the control oil return line 9, closed by a closure member. This is a technique known with stackable control blocks and therefore not shown.
  • the power of the pump 4 is determined by the prevailing load pressure. It depends on the maximum load pressure.
  • the consumers 1.1 or 1.2 generally have different load pressures. They are sensed in a known manner to the directional valves 11.1 and 11.2 and passed from the shuttle valves 16.1 and 16.2 to the load pressure signaling lines 17.1 and 17.2. If the pressure in the load pressure signaling line 17.1 higher than in the load pressure line 8, then this higher pressure would open the check valve 18.1, so that in the load pressure line 8 then the higher pressure prevails. This applies analogously to the load pressure signaling line 17.2 and the check valve 18.2. This is known technique.
  • the 2/2-way proportional valve 15.1 is connected on the one hand to the pump line 6, is thus controlled by the pressure prevailing in the pump line 6 pump pressure, and on the other hand connected to the load pressure line 8, so that it is in the load pressure line 8 prevailing maximum load pressure of the consumer 1 is controlled.
  • the pump pressure acts against a control spring 20.1.
  • throttle bodies are arranged in control lines for the directional control valve 11.1.
  • a control line 23.1 to the left control terminal of the directional control valve 11.1 and in a control line 24.1 connected in series to the right control port of the directional control valve 11.1 in series two throttling points, namely in the control line 23.1 a first pressure divider throttle body 30.1 and a first damping throttle body 31.1 and in the control line 24.1, a second pressure divider throttle 40.1 and a second damping throttle 41.1.
  • the slide of the 2/2 -Wege- proportional valve 15.1 is arranged with its control edges as another effective throttle point.
  • control lines of the 2/2-way proportional valve 15.1 that is arranged in the connection to the pump line 6 on the one hand and in the connection to the load pressure line 8, depending on a further throttle point.
  • this is a first control piston damping throttle 45.1
  • a second control piston damping throttle 46.1 in the course of the load pressure line 8
  • This applies equally to the 2/2-way proportional valve 15.2, in which the control piston Dämpfungsdrosselstellen 45.2 and 46.2 are present.
  • Throttles 45.1 and 46.1 or 45.2 and 46.2 can be the response of the 2/2-way proportional valves 15.1 and 15.2 optimize. Thus, for example, control vibrations can be prevented.
  • FIG. 2 corresponds in terms of their construction of FIG. 1 with the difference that the drive 1.2 is shown here as the drive 1.1 as a double-acting drive cylinder.
  • the difference between Figs. 1 and 2 further consists in that in Fig. 1, the basic position of the valves is shown, while Fig. 2 shows a specific operating condition.
  • the first proportional pressure reducing valve 13.1 is actuated by the operator in order to move the drive 1.1, this valve opens and allows the flow of the pressure medium from the pump line 6 into the control line 23.1 and further via the throttle points 30.1 and 31.1 to the left control connection of the directional control valve 11.1, which is thus turned on and moves the drive 1.1.
  • the control of the proportional pressure reducing valve 13.1 is indicated by an arrow Al on the electromagnetic drive.
  • the pressure medium flowing in the control line 23.1 acts on the left hydraulic drive of the directional control valve 11.1. This now assumes the position shown, can flow in the pressure fluid from the pump line 6 through the directional control valve 11.1 to the rod side of the drive 1.1. At the same time can flow from the piston chamber of the drive 1.1 pressure fluid via the directional control valve 11.1 in the tank line 7.
  • the piston of the drive 1.1 thus moves to the left.
  • the 2/2 -way proportional valve 15.1 now has a position that results from the ratio of pump track and maximum load pressure.
  • the 2/2-way proportional valve 15.1 has a specific throttling effect, which is also determined by the spring 20.1.
  • the 2/2-way proportional valve 15.1 is closed, so that the outflow of pressure medium into the tank 5 is prevented, so that the control pressure of the first proportional pressure reducing valve 13.1 fully on the directional control valve 11.1 acts. This is the case with sufficient pump delivery. However, if the pump pressure falls below a certain value, which occurs when the pump 4 can not supply the required pressure medium flow, then pressure medium flows into the tank 5 in the previously described manner.
  • FIG. 1 a schematic of the effective pressure divider is shown in FIG. From the circuit of Fig. 1 and 2, therefore, those parts are drawn out separately, which make up the effect of the pressure divider chain. From left to right, the three effective components of the pressure divider are shown, namely the first pressure divider throttle body 30.1, the throttle point X 15J5 denoting the throttle effect of the 2/2 -way proportional valve 15.1, and the second pressure divider throttle 40.1. On the left side of this component chain is the
  • This output control pressure is for example a maximum of 20 bar.
  • Control oil return line 9 is identical to the pressure in the tank line 7, ie is at zero pressure tank 5 (Fig. 2) 0 bar.
  • the effective throttle cross-sections shown which are converted for simplicity to a certain diameter in mm.
  • the effective throttle diameter of the first pressure divider throttle body 30.1 is for example 0.45 mm, that of the throttle point Xi 5-1 0.40 mm and that of the second pressure divider throttle point 40.1 0.35 mm. From this, it is now possible to calculate which pressure drops occur across the individual throttle points.
  • the exemplary numerical values for the pressures show on the left of the first pressure divider orifice 30.1 a pressure of 20 bar and on the right a pressure of 16 bar.
  • Pressure reducing valves 13.1 or 14.1 or 13.2 or 14.2 generated control pressure thus acts in each case in full size on the corresponding side of the directional control valves 11.1 and 11.2.
  • control device 2 is designed so that the pump pressure is 25 bar higher than the maximum load pressure. But now the pump pressure drops because of the demand of a pressure medium flow through the consumer, which is higher than that
  • the 2/2-way proportional valve 15.1 is controlled so that a portion of the control oil flow for the directional control valve 11.1 flows into the tank 5. This reduces the control pressure of the directional control valve 11.1, which has the consequence that the speed of the drive 1.1 is reduced so much that now the pressure medium to be supplied by the pump 4 is reduced so that the design difference between pump pressure and maximum load pressure of 25 bar is reached again.
  • the 2/2-way proportional valve 15.1 also now has a position that results from the ratio of pump pressure and maximum load pressure. Accordingly, the 2/2-way proportional valve 15.1 has a specific throttle effect. Thus, part of the flowing from the proportional pressure reducing valve 14.1 in the control line 24.1 pressure fluid via the pressure divider throttle body 30.1 and the slide of the non-actuated proportional valve 13.1 in the control oil return line 9 and thus in the tank 5 from. In this way, the control of the directional control valve 11.1 is reduced and indeed as a function of the ratio of pump pressure and maximum load pressure.
  • the pressure divider chain acts as described above. The higher the maximum load pressure compared to the pump pressure, the stronger the control of the directional control valve 11.1 is reduced.
  • the throttling effect of the 2/2-way proportional valve 15.1 is also determined by the spring 20.1. This also applies to the 2/2-way proportional valve 15.2 and the spring 20.2. Do the springs 20.1 and 20.2 have the same Spring rate, the throttle effect of the two 2/2-way proportional valves 15.1 and 15.2 is the same. If the spring rates are different, the throttling effect is not the same. This opens up the possibility, in a simple manner by the choice of different spring rates or by the adjustability of the spring rate of the springs 20.1 and / or 20.2 a priority, so a priority to realize for one of the consumers.
  • FIG. 4 shows a scheme with a circuit supplement.
  • This diagram shows a section of FIGS. 1 and 2, namely the part with the directional control valve 11.1, the 2/2-way proportional valve 15.1 and the throttle bodies 30.1, 31.1, 40.1 and 41.1.
  • the circuit supplement is that in the control line, which leads from the connection point of the throttle bodies 30.1 / 31.1 via the 2/2-way proportional valve 15.1 to the connection point of the throttle bodies 40.1 / 41.1, an anti-parallel circuit 50 of two biased check valves 51.1 and 52.1 is arranged.
  • the biased check valves 51.1 and 52.1 are advantageously designed so that they open at a pressure difference of 5 bar. Only when the control pressure for the directional control valve 11 is more than 5 bar above the tank pressure, thus, the previously described reduction of the control of the directional control valve 11 can be effective. This will now be shown again with reference to a figure showing the chain of effective throttle points. This is shown in FIG. 5.
  • FIG. 5 corresponds to FIG. 3, but additionally contains the anti-parallel circuit 50 of the two preloaded check valves 51.1 and 52.1 (FIG. 4).
  • control blocks 3 contain an upstream pressure compensator and also a controllable
  • Pressure divider with the help of which a part of the control flow for the directional control valve 11.1 or 11.2 is derivable into the tank, if the highest load pressure is greater than the sum of pump pressure and a minimum difference of 25 bar, for example, by means of the 2/2-way Proportional valve 15.1 or 15.2 can be detected and controlled.
  • control device 2 with its control blocks 3.1, 3.2 and optionally further control blocks 3.n thus automatically compensates for an undersupply. It can therefore be used advantageously not only when it is to be expected in a working device with a shortage, but in principle even if interpretatively with a shortage does not have to be expected. Should a deficiency occur in adverse circumstances nevertheless, then the

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Abstract

La présente invention concerne un dispositif de commande pour au moins deux commandes hydrauliques qui peuvent être commandées au moyen de blocs de commande (3.1; 3.2). Ces commandes hydrauliques peuvent se commander au moyen de vannes de distribution (11.1; 11.2) commandées quant elles par des vannes de détente proportionnelles (13.1, 14.1; 13.2, 14.2) servant de vannes pilotes. Selon l'invention, les blocs de commande (3.1; 3.2) comprennent un régulateur de pression (12.1; 12.2) monté en amont et un répartiteur de pression commandé. Le répartiteur de pression est un binôme constitué, d'une part d'une vanne proportionnelle 2/2 voies à commande hydraulique (15.1; 51.2), montée entre les vannes de détente proportionnelles (13.1, 14.1; 13.2, 14.2) et les entrées de commande hydraulique des vannes de distribution (11.1; 11.2), et d'autre part des étranglements (30.1, 40.1; 30.2, 40.2). Il est possible de monter en série plusieurs de ces blocs de commande pour commander plusieurs charges, ce qui permet d'éviter les effets néfastes d'une alimentation insuffisante, sans avoir besoin d'autres composants externes.
EP08772899A 2007-08-02 2008-07-23 Dispositif de commande pour au moins deux commandes hydrauliques Withdrawn EP2171289A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH01229/07A CH700344B1 (de) 2007-08-02 2007-08-02 Steuervorrichtung für mindestens zwei hydraulische Antriebe.
PCT/CH2008/000328 WO2009015502A1 (fr) 2007-08-02 2008-07-23 Dispositif de commande pour au moins deux commandes hydrauliques

Publications (1)

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EP2171289A1 true EP2171289A1 (fr) 2010-04-07

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EP (1) EP2171289A1 (fr)
CH (1) CH700344B1 (fr)
WO (1) WO2009015502A1 (fr)

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CN103062140B (zh) 2013-01-17 2014-01-08 江苏恒立高压油缸股份有限公司 基于合流控制方式的液压装置
DE102014216034A1 (de) * 2014-08-13 2016-02-18 Robert Bosch Gmbh Ventilanordnung mit verstellbarer Lastrückmeldung
DE102015122929A1 (de) 2015-12-29 2017-06-29 Xcmg European Research Center Gmbh Steuerung für ein hydraulisch betätigbares Ventil
DE102015122930A1 (de) 2015-12-29 2017-06-29 Xcmg European Research Center Gmbh Steuerung für ein hydraulisch betätigbares Ventil
DE102016215214A1 (de) 2016-08-16 2018-02-22 Zf Friedrichshafen Ag Getriebevorrichtung mit mehreren über hydraulisch betätigbare Kolben-Zylinder-Einrichtungen verstellbare Schaltstangen ein- und auslegbaren Übersetzungen
CN106382271B (zh) * 2016-10-18 2017-12-26 浙江大学 一种高速开关阀先导控制的双阀芯可编程控制液压阀及其方法
DE102023205767B3 (de) 2023-06-20 2024-06-20 Hawe Hydraulik Se Hydraulikventilverband und Mobilhydraulik

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FR2553475B1 (fr) * 1983-10-17 1988-03-04 Poclain Sa Circuit d'alimentation en fluide sous pression comportant une pompe a cylindree variable
DE3603630A1 (de) * 1986-02-06 1987-08-13 Rexroth Mannesmann Gmbh Steueranordnung fuer mindestens zwei von mindestens einer pumpe gespeiste hydraulische verbraucher
US4858649A (en) * 1986-09-09 1989-08-22 Hitachi Construction Machinery Co., Ltd. Valve apparatus
DE3890121C2 (de) * 1987-02-20 1996-08-08 Hitachi Construction Machinery Hydraulisches Schnellablaßventil und hydraulischer Fernsteuerungskreis mit einem solchen Schnellablaßventil
JP2002005109A (ja) * 2000-06-16 2002-01-09 Hitachi Constr Mach Co Ltd 操作制御装置
JP3557167B2 (ja) * 2000-11-20 2004-08-25 新キャタピラー三菱株式会社 作業用機械における油圧回路
DE10321914A1 (de) * 2003-05-15 2004-12-02 Bosch Rexroth Ag Hydraulische Steueranordnung
JP2006125627A (ja) * 2004-09-29 2006-05-18 Kobelco Contstruction Machinery Ltd 建設機械の油圧回路

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Also Published As

Publication number Publication date
WO2009015502A1 (fr) 2009-02-05
CH700344B1 (de) 2010-08-13

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