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EP1875084A1 - Directional control valve and control system provided therewith - Google Patents

Directional control valve and control system provided therewith

Info

Publication number
EP1875084A1
EP1875084A1 EP06722721A EP06722721A EP1875084A1 EP 1875084 A1 EP1875084 A1 EP 1875084A1 EP 06722721 A EP06722721 A EP 06722721A EP 06722721 A EP06722721 A EP 06722721A EP 1875084 A1 EP1875084 A1 EP 1875084A1
Authority
EP
European Patent Office
Prior art keywords
valve
control
pressure
chamber
slide
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06722721A
Other languages
German (de)
French (fr)
Other versions
EP1875084B1 (en
Inventor
Heinrich Lödige
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.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth 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 Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1875084A1 publication Critical patent/EP1875084A1/en
Application granted granted Critical
Publication of EP1875084B1 publication Critical patent/EP1875084B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F15B11/02Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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
    • 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
    • F15B11/02Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • 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
    • F15B13/00Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01Locking-valves or other detent i.e. load-holding devices
    • 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
    • F15B13/00Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/021Valves for interconnecting the fluid chambers of an actuator
    • 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
    • F15B13/00Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401Valve members; Fluid interconnections therefor
    • F15B13/0402Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
    • F15B13/00Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation 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
    • F15B13/00Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043Fluid 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
    • F15B13/0433Fluid 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

Definitions

  • the invention relates to a directional control valve with two guided in a slide bore coaxially arranged valve spools according to the preamble of patent claim 1 and an executed with such a directional control valve LS control arrangement.
  • directional valves are often required with four slide positions, in addition to a neutral position in which a pressure port and two working ports are shut off and a floating position in which the two working ports are connected to a tank connection two more working positions must be taken from the directional control valve, in which one working connection with the pressure connection and the other working connection with the return connection and in the other positions according to the former working connection with the tank connection and the further working connection is connected to the pressure connection.
  • valves with two valve slides are known from the prior art, which are accommodated in a common valve housing bore.
  • the applicant's EP 1 500 825 A2 discloses a solution in which the two valve slides are spaced apart from one another via a central spring, wherein the maximum distance between the two valve slides is limited by a pull rod or the like.
  • a directional control valve with two coaxial valve slides is disclosed in Fig. 10, in which the two valve spools are arranged directly without interposed spring. However, the operation is also by means of electromagnets.
  • Fig. 12 shows a Embodiment in which the actuation is performed hydraulically, to the rear control surfaces of the two valve spools is assigned in each case a drive piston which is designed with two control surfaces whose surfaces are designed with the ratio 1: 2. In the basic position, the smaller area is correspondingly charged with twice the control pressure. The shifting takes place in which the control pressure acting on one of the control surfaces is lowered or lowered.
  • a disadvantage of this solution is that the drive pistons fixedly connected to the valve slide are comparatively complicated and that only half the control pressure is available for the axial displacement of the valve slide into the working positions, so that the resolution is correspondingly low.
  • the invention has for its object to provide a directional control valve and a LS-control arrangement designed therewith, which is designed to be simple and compact and allows an accurate displacement of the valve spool in predetermined working positions.
  • the directional valve is formed with two coaxially arranged valve spools, which are directly, ie, without the interposition of a spring or a tie rod or the like in abutment with each other.
  • the adjacent end faces of the valve slide can be acted upon with the same control pressure as rear control surfaces, the effective area, however, is smaller than that of the end faces.
  • a predetermined slide position for example, a floating position. Accordingly, in the solution according to the invention neither directly on the valve spool engaging electrical components (such as plunger of an electromagnet) required for the shift, nor must a component be provided between the two valve spools to limit the stroke.
  • the adjustment in the predetermined slide position is due to the area difference, wherein the end faces and the control surfaces are acted upon by the same control pressure, so that the channel guide over the conventional solutions is substantially simplified.
  • this surface difference is formed by flasks that dip into the rear end portions of the valve spool and which are supported on the housing. These flasks limited with the respective valve spool a piston chamber which is acted upon by the control pressure.
  • the end portions of the valve spools are radially recessed and each dive into a cap, with the spigot faces forming the control surfaces of reduced cross-section.
  • Such a construction is known per se from DE 3732445 A1 (FIG. 5).
  • the bias of the two valve spool in its basic position for example, via two each received in a spring chamber centering springs, which engage in each case at a rear end portion of the valve spool.
  • the spring chamber accommodating the centering spring is subjected to tank pressure.
  • everyone from the valve spool and Kolbchen limited piston chamber is preferably connected via at least one shell breakthrough, leading to a control pressure control chamber of the valve bore and acted upon by a shift with tank pressure.
  • the structure of the directional control valve is particularly simple when this shell breakthrough connects the piston chamber with the spring chamber after the displacement of the valve spool.
  • two tank chambers leading to the tank or return pressure are arranged on the outside in the valve bore, so that two pressure chambers connected to a pressure connection and two working chambers connected to one working connection and a central central control chamber acted upon by the control pressure and optionally further control chambers are arranged between the tank chambers.
  • the central control chamber is connected in the basic position via an inverse shuttle valve with the piston chambers of the valve spool, so that in the central control chamber always the lower of the control pressures is applied.
  • the hydraulic control of the directional control valve is preferably carried out by two proportionally acting pressure reducing valves, via which the control surfaces of the two valve spool can be acted upon by the control pressure and connect the control surfaces in their basic position with tank pressure and thus relieve.
  • the LS control arrangement is preferably carried out with an individual pressure compensator and at least one work connection assigned a blocking block.
  • FIG. 2 shows a concrete embodiment of the LS control arrangement according to FIG. 1 in the neutral position
  • Fig. 3 is an enlarged view of the valve spool of the directional control valve of Fig. 2;
  • FIG. 4 shows the embodiment according to FIG. 2 in a working position
  • Fig. 5 shows the embodiment of FIG. 2 in a floating position
  • Fig. 6 shows a further concrete embodiment of an LS control arrangement according to the invention.
  • valve disk 1 shows a circuit diagram of a valve disk of a LS mobile control block, via which hydraulic consumers of a tractor can be controlled.
  • the valve disk 1 has two working ports A, B, which lead, for example, to the two pressure chambers of a hydraulic cylinder, a pressure port P, two drain or tank ports Rl and R2, an LS port LS, a control pressure port Px and a tax return port Rx.
  • the basic structure of such LS control arrangements in applications in mobile hydraulics is essentially the same, they include a proportionally adjustable directional control valve 2, which contains a speed part and a direction part for adjusting the pressure medium volume flow to or from the consumer.
  • the directional control valve 2 with two valve spools 4,
  • valve slide assembly via two electrically actuated pressure reducing valves 12, 14, whose input port P to the control pressure port Px, at which a relatively high input control pressure is applied and whose tank port T is connected to the control return port Rx.
  • the output port A of the pressure reducing valves 12, 14 is connected to the control side of the respective associated valve spool 4 and 6 respectively.
  • the speed part of the directional control valve 2 is formed in each case by an orifices 16, 18 formed by control edges of the valve spool 4, 6, to which an individual pressure compensator 20 is connected upstream. This is acted upon in the sense of an enlargement of the opening cross section by the force of a pressure compensator spring 22 and the load pressure of the associated consumer, which rests on an LS channel 26 at the effective in the opening direction control surface of the pressure compensator 20.
  • the load pressure of the consumers driven via the other valve disks of the LS mobile pressure is applied via the control connection Y 1 to the input of a shuttle valve 24 and compared with the load pressure of the consumer connected to the valve disk, the largest load pressure is then tapped off at the LS connection.
  • the larger of the load pressures at the working ports A, B is tapped via another shuttle valve 28, at the output of the LS channel 26 is connected.
  • the pressure compensator 20 is acted upon by the pressure in the pressure medium flow path between the pressure compensator 20 and the directional control valve 2.
  • the pressure compensator 20 holds in its control position the pressure drop above the adjusted metering orifice 16, independent of load pressure, constant.
  • the highest load pressure of all controlled by the mobile control block consumer is led to a pump governor of a variable or bypass pressure compensator of a constant pump, whereby the pump pressure in a pump line is adjusted so that it always by a predetermined ⁇ p above this maximum load pressure lies.
  • the two valve slides 4, 6 can be moved out of the illustrated basic position against the force of the centering springs 8, 10 to the outside.
  • the mutually facing end faces of the valve slide 4, 6 project into a common central pressure chamber 30, which is acted upon by the output pressure of the pressure reducing valves 12 or 14.
  • these pressure reducing valves 12, 14 are set to different control pressures, the smaller of these control pressures is tapped via an inverse shuttle valve 32 and forwarded to the central control pressure chamber 30 connected to the output of this inverse shuttle valve 32. If both pressure reducing valves 12, 14 are set to the same control pressure, this control pressure is also present in the central control pressure chamber 30.
  • a blocking block 34, 36 is provided in the pressure medium flow path between the directional control valve and the associated working ports A, B, whose structure is explained in more detail with reference to FIG.
  • Such blocking blocks 34, 36 allow a flow of pressure medium to the associated working port A, B.
  • the locking block 34, 36 can be unlocked by means of a poppet piston. When pulling loads this lock block 34, 36 then acts as Pressure compensator, which makes it possible to carry out a load pressure-independent pressure medium control with the drain metering orifice 38, 40 controlled via the directional control valve.
  • Fig. 2 shows a concrete embodiment of the valve disc 1 of a mobile control block.
  • This valve disk 1 is traversed in the transverse direction by a valve bore 42, in which the two valve spools 4, 6 are guided axially displaceably.
  • the two valve slides are biased via the centering springs 8, 10 in an abutment position in which the end faces 44, 46 of the valve slide 4, 6 abut each other.
  • the centering springs 8, 10 are supported on the valve bore 42 axially final spring caps 48, 50, each delimiting a spring chamber in which always the tank or return pressure is applied, the above the in Fig. 2 adjacent to the spring chamber, shown only in cross section Channel is tapped.
  • each piston chamber 52 and 54 is formed, wherein the piston chamber of the valve spool 6 is indicated only by dashed lines.
  • the piston chambers 52, 54 each have a piston 56, 58 is inserted, the are supported with a protruding from the valve spool 4, 6 end portion at the bottom of the spring cap 48 and 50 respectively.
  • the flasks 56, 58 close the two piston chambers 52, 54 in the axial direction pressure medium-tight.
  • the bottom surfaces of each piston chamber 52, 54 each form a control surface 60, 62 whose effective area is less than the cross-sectional area of the end face 44, 46 of the respective valve slide 4 and 6.
  • control surfaces 60, 62 designed with lower effective surfaces can also be formed in kinematic reversal, in which the end sections of the valve spools 4, 6 are recessed in the form of pegs and immersed in caps, so that a respective cap and an end section is formed by the control surface 60, 62 limited space, which can be acted upon by channels in the valve slide 4, 6 with the control pressure or tank pressure.
  • two external tank chambers 72, 74, two working chambers 76, 78, two inlet chambers 80, 82, two control pressure chambers 84, 86, two control chambers 88, 90 arranged inside thereof and the central central control chamber 92 is formed.
  • the two tank chambers 72, 74 are connected via channels, not shown, with the spring chambers and the two return connections Rl, R2 (FIG. 1) of the valve disk 1.
  • the two inside arranged working chambers 76, 78 lead via a flow channel 94 to the working port A. or via a return channel 96 to the working port B.
  • the two inlet chambers 80, 82 are connected to each other via an inlet channel 98 into which the output of the individual pressure compensator 20 opens, the input via a pressure compensator input chamber 100 to the pressure port P (Fig 1 is connected.
  • a compression chamber spring 22 receiving spring chamber 102 of the pressure compensator 20 is connected via the LS channel 26 to the output of the shuttle valve 24 and further guided to the output of the further shuttle valve 28, the two inputs via an approximately U-shaped connecting channel 104 with the working chamber 76 and 78 are connected.
  • the input ports P of the two pressure reducing valves 12, 14 are connected to the control pressure port Px and their tank ports T are connected to the control return port Rx.
  • the two output ports A are fed via pilot control channels 106, 108 to the inputs of the inverse shuttle valve 32, the output of which is connected to the central control chamber 92.
  • FIG. 3 As in particular the enlarged view of the two valve spool 4, 6 as shown in FIG. 3 can be removed, are formed on these from the outside to the inside tank control edges 110, 112, inlet control edges 114, 116, control edges 118, 120 and further control edges 158, 159, each of Peripheral edges of a piston collar are formed. As further Fig. 3 can be removed, open the jacket holes 64, 68 in the pilot channel 106 and 108, the two other shell bores 66, 70 are covered in the basic position.
  • the two blocking blocks 34, 36 are inserted as shown in FIG. 2 in the flow channel 94 and the return channel 96.
  • You have a running with a pilot opening closing body 122 and 124, each of a Closing spring 126, 128 is biased against a valve seat 130, 132.
  • a pilot valve body 134, 136 is received and biased against another pilot valve seat.
  • Each pilot valve body 134, 136 can be lifted off its pilot valve seat by means of a poppet piston 138, 140 by applying a control pressure to its piston surface 142, 144.
  • the piston surface 142, 144 limits a pressure chamber, which is connected via control channel sections 146, 148 to the two control chambers 88, 90, which are connected to the central control chamber 92 via the further control edges 158, 159.
  • a spring chamber 150, 152 of the blocking block 34, 36 is connected to the pilot channel 106, 108 via a short channel section.
  • the spring chamber 150, 152 is further connected to the working port A, B.
  • the pressure medium flows via the individual pressure compensator 20 and arrives in the inlet channel 98.
  • the two pressure reducing valves 12, 14 are de-energized, so that the two pilot control channels 106, 108 are relieved to the return port Rx.
  • the two piston surfaces 142, 144 of the poppet pistons 138, 140 are also relieved to the return port Rx.
  • the two slides 4, 6 take due to the bias of the centering springs 8, 10 their illustrated center position in which the control edges 112, 114 and 116, 118 shut off the pressure medium connection of the working ports A, B to the pressure port P and to the return ports Rl and R2.
  • the two working chambers 76, 78 and thus the flow channel 94 and the return channel 96 are respectively formed in the valve slide 4 and 6 connecting bores 154, 156 (dashed lines in Figures 2 and 3) with the tank chambers 72, 74 and thus with the return ports Rl and R2, and thus if pressure relieved.
  • the load pressure signal which is tapped via the connecting channel 104 and arranged therein another shuttle valve 28 is then corresponding to this valve disc 1 also at tank pressure level.
  • the two locking blocks 34, 36 are locked because the two valve bodies 122, 124 are pressed by the respective load pressure and the closing springs 126, 128 against the associated valve seats 130, 132.
  • the pressure reducing valve 12 is energized.
  • the control pressure which is proportional to the supply of the pressure reducing valve is guided via the output port A of the pressure reducing valve 12, the pilot passage 108 and the shell bores 70 and - after an axial displacement of the valve spool - 68 in the left piston chamber 54.
  • the right piston chamber 52 is - as in the neutral division - still relieved via the no-load pressure reducing valve 14 to return R x out. Accordingly, the tank pressure is also present in the right pilot control channel 106.
  • the set via the pressure reducing valve 12 control pressure is applied to the left input of the inverse shuttle valve 32, while at its right input via the pilot passage 106, the tank pressure is applied - the inverse shuttle valve 32 is thus opened to the tank pressure, so that it acts in the central control chamber 92 ,
  • the two valve spool 4, 6 are moved by the pressure on the control surface 62 as shown in FIG. 4 to the right, wherein the piston 58 is further supported on the spring cap 50.
  • the stroke of the valve slide 4, 6 is determined by the diameter of the piston 58, the surface of the control surface 62, the force of the centering spring 8 and the size of the pressure reducing valve 12th set control pressure. Due to the axial displacement to the right, the connection from the inlet chamber 82 to the working chamber 78 is opened via the inlet control edge 116 so that the pressure medium can flow from the outlet of the pressure compensator 20 into the inlet channel 94.
  • the now acting as a check valve body 124 is lifted from its valve seat 132 and released the pressure medium flow to the working port A.
  • the piston surface 144 of the poppet 140 is acted upon by the central control chamber 92 and the inverse shuttle valve 32 with tank pressure.
  • the connection of the control chamber 88 is shut off with the pressure-relieved central control chamber 92 and via the control edge 118 opens a connection with the input control pressure of the pressure reducing valve 12, 14 leading control pressure chamber 84, so that the piston surface 42 of the poppet 138 with the high input control pressure of the pressure reducing valve 12 is acted upon.
  • the poppet 138 is thereby moved to the right in FIG.
  • valve body 122 follows the pilot valve body 134 and the pressure medium can flow from the consumer via the working port B, the return channel 96 and the controlled by the tank control edge 110 connection between the working chamber 76 and the tank chamber 72 to the return port R2 ,
  • the pressure at the fuel tank Edge 110 and thus rests in the return channel 96 acts on the topping piston 138, so that this acts together with the valve body 130 of the locking block 34 as a discharge pressure compensator, which keeps the discharge pressure at the tank control edge 110 of the valve spool 4 constant, and thus pulling
  • both pressure reducing valves 12, 14 are energized, so that at their outputs A, the same output control pressure is set .
  • This output control pressure of the two pressure reducing valves 12, 14 is then via the pilot control channels 106, 108 also at the two inputs of the inverse exchange valve 32 and to the control surfaces 60, 62 of the piston chambers 52, 54 (see FIG. 2). Since the same output control pressure is present at both inputs of the inverse shuttle valve 32, the central control chamber 92 is also subjected to this pressure.
  • Both check valves 34, 35 are - as in the context in Fig. 4 - opened and thus the two working ports A, B via the flow channel 94, the return channel 96, the two working chambers 76, 78, the tank control edges 110, 112 and the outer tank chambers 72, 74 connected to the return ports R1 / R2.
  • the inlet control edges 114, 116 block the connection to the inlet channel 98 and thus to the output of the pressure compensator 20 - the floating position is set.
  • the LS control arrangement can be formed with only one blocking block 34, the channel guidance substantially corresponding to the above-described embodiment, with the exception that now the connecting channel 104, via which the load pressure is tapped no longer leads to the working chamber 78 but to a chamber 160 which in the illustrated basic position on the slightly longer than in the previously described embodiments executed connecting bore 156 with the left tank chamber 74 is connected.
  • the connection to the control chamber 90 is then opened via an additional control edge 162, via which the load pressure at the working connection A is then reported to the connection channel 104. That is, the chambers on the valve spool 4, 6, which serve in the use of blocking blocks for controlling the impact pressure, are used in this embodiment for tapping off the load pressure.
  • the two valve slides 4, 6 are correspondingly no longer identical.
  • shut-off valves and the individual pressure compensator can be omitted.
  • a directional control valve and a LS Steueran- wherein the directional control valve is designed with two coaxial with each other arranged VentilSchiebern whose adjacent end faces are larger than rear control surfaces are formed and can be brought directly into contact with each other.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Analytical Chemistry (AREA)
  • Chemical & Material Sciences (AREA)
  • Multiple-Way Valves (AREA)
  • Servomotors (AREA)
  • Valve Device For Special Equipments (AREA)
  • Float Valves (AREA)
  • Massaging Devices (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

The valve has two slides (4, 5) which are spring-loaded towards the center of a bore (42). The slides share a common control system which allows pressure to be applied simultaneously to their front surfaces (44, 46) and to their rear surfaces (60, 62), which are smaller in area. An independent claim is included for LS-control systems for hydraulic fluid which contain the valve.

Description

Beschreibung Wegeventil und damitausgeführte LS-Steueranordnung Description Directional control valve and LS control system implemented therewith
Die Erfindung betrifft ein Wegeventil mit zwei in einer Schieberbohrung geführten koaxial zueinander angeordneten Ventilschiebern gemäß dem Oberbegriff des Patentanspruchs 1 und eine mit einem derartigen Wegeventil ausgeführte LS-Steueranordnung.The invention relates to a directional control valve with two guided in a slide bore coaxially arranged valve spools according to the preamble of patent claim 1 and an executed with such a directional control valve LS control arrangement.
Insbesondere in der Mobilhydraulik werden häufig Wegeventile mit vier Schieberstellungen benötigt, wobei neben einer Neutralstellung, in der ein Druckanschluss und zwei Arbeitsanschlüsse abgesperrt sind und einer Schwimmstellung, in der die beiden Arbeitsanschlüsse mit einem Tankanschluss verbunden sind noch zwei weitere Arbeitspositionen vom Wegeventil eingenommen werden müssen, bei denen einmal ein Arbeitsanschluss mit dem Druckanschluss und der andere Arbeitsanschluss mit dem Rücklaufanschluss und in den anderen Positionen entsprechend der erstgenannte Arbeitsanschluss mit dem Tankanschluss und der weitere Arbeitsanschluss mit dem Druckanschluss verbunden ist.Especially in mobile hydraulics directional valves are often required with four slide positions, in addition to a neutral position in which a pressure port and two working ports are shut off and a floating position in which the two working ports are connected to a tank connection two more working positions must be taken from the directional control valve, in which one working connection with the pressure connection and the other working connection with the return connection and in the other positions according to the former working connection with the tank connection and the further working connection is connected to the pressure connection.
Derartige herkömmliche Wegeventile werden mit einem HauptSchieber ausgeführt, wobei die Steuerfunktionen in den Weg dieses Schiebers gelegt werden. Dies hat einige Nachteile, da beispielsweise zum Erreichen der Schwimmstellung eine Arbeitsstellung vollständig überfahren werden muss. Der dafür erforderliche große Schieberhub führt zu einem relativ langem Schieber und damit zu einem entsprechend langem Ventilgehäuse.Such conventional directional valves are carried out with a main slide, wherein the control functions are placed in the path of this slide. This has some disadvantages, since, for example, to reach the floating position a working position must be completely overrun. The required large spool stroke leads to a relatively long slide and thus to a correspondingly long valve body.
Bei einer elektrohydraulisehen Betätigung wird die häufig für eine längere Zeit eingestellte Schwimmstellung in der Endposition des Schiebers angesteuert. Dies erfordert, dass, der Ventilschieber mit einem ständigen hohem Steuerdruck beaufschlagt ist, so dass entsprechend auch ein hoher elektrischer Eingangsström gehalten werden muss . Des Weiteren wird die Auflösung für den Schieberhub in seinen Arbeitsstellungen gemindert, da ein Teil des Steuerdruckbereichs für die Schwimmstellung benötigt wird.In a elektrohydraulisehen operation often set for a longer time floating position is driven in the end position of the slider. This requires that, the valve spool with a constant high Control pressure is applied, so that accordingly a high electrical Eingangsström must be maintained. Furthermore, the resolution for the spool stroke is reduced in its working positions, since a part of the control pressure range is required for the floating position.
Zur Beseitigung zumindest einiger dieser Nachteile sind aus dem Stand der Technik Wegeventile mit zwei Ventilschiebern bekannt, die in einer gemeinsamen Ventil- gehäusebohrung aufgenommen sind. Die EP 1 500 825 A2 der Anmelderin offenbart beispielsweise eine Lösung, bei der die beiden Ventilschieber über eine Zentralfeder voneinander beabstandet sind, wobei der maximale Abstand zwischen den beiden VentilSchiebern durch eine Zugstange oder dergleichen begrenzt ist.To eliminate at least some of these disadvantages, valves with two valve slides are known from the prior art, which are accommodated in a common valve housing bore. The applicant's EP 1 500 825 A2, for example, discloses a solution in which the two valve slides are spaced apart from one another via a central spring, wherein the maximum distance between the two valve slides is limited by a pull rod or the like.
Ähnliche Lösungen sind in der EP 0 114 470 Bl und der EP 0 573 191 Bl offenbart, bei denen das Wegeventil ebenfalls mit zwei koaxial zueinander angeordneten Ventilschiebern ausgeführt ist, zwischen denen eine Feder vorgesehen ist .Similar solutions are disclosed in EP 0 114 470 Bl and EP 0 573 191 B1, in which the directional control valve is also designed with two coaxially arranged valve slides, between which a spring is provided.
Derartige Lösungen sind vergleichsweise aufwendig, da die Feder in geeigneter Weise aufgenommen werden muss. Nachteilig bei den in der EP 0 114 470 Bl und der EP 0 573 191 Bl gezeigten Lösungen ist des Weiteren, dass die Verstellung der Ventilschieber mittels Elektromagneten und davon betätigter Stößel erfolgt, so dass der vorrichtungstechnische Aufwand weiter erhöht ist.Such solutions are relatively expensive, since the spring must be taken in a suitable manner. A disadvantage of the solutions shown in EP 0 114 470 Bl and EP 0 573 191 Bl is further that the adjustment of the valve slide by means of electromagnets and operated therefrom plunger, so that the device complexity is further increased.
In der WO 02/075162 Al ist in Fig. 10 ein Wegeventil mit zwei koaxialen Ventilschiebern offenbart, bei denen die beiden Ventilschieber unmittelbar ohne dazwischen geschaltete Feder angeordnet sind. Die Betätigung erfolgt jedoch auch mittels Elektromagneten. Fig. 12 zeigt ein Ausführungsbeispiel, bei dem die Betätigung hydraulisch erfolgt, dazu ist den rückwärtigen Steuerflächen der beiden Ventilschieber jeweils ein Antriebskolben zugeordnet, der mit zwei Steuerflächen ausgeführt ist, deren Flächen mit dem Verhältnis 1:2 ausgeführt sind. In der Grundposition wird die kleinere Fläche entsprechend mit dem doppelten Steuerdruck beaufschlagt . Das Verschieben erfolgt, in dem der auf eine der Steuerflächen lastende Steuerdruck abgesenkt oder erniedrigt ist. Nachteilig bei dieser Lösung ist, dass die mit dem Ventilschieber fest verbundenen Antriebskolben vergleichsweise aufwendig ausgebildet sind und dass für die Axialverschiebung der VentilSchieber in die Arbeitspositionen nur der halbe Steuerdruck zur Verfügung steht, so dass entsprechend die Auflösung gering ist.In WO 02/075162 Al a directional control valve with two coaxial valve slides is disclosed in Fig. 10, in which the two valve spools are arranged directly without interposed spring. However, the operation is also by means of electromagnets. Fig. 12 shows a Embodiment in which the actuation is performed hydraulically, to the rear control surfaces of the two valve spools is assigned in each case a drive piston which is designed with two control surfaces whose surfaces are designed with the ratio 1: 2. In the basic position, the smaller area is correspondingly charged with twice the control pressure. The shifting takes place in which the control pressure acting on one of the control surfaces is lowered or lowered. A disadvantage of this solution is that the drive pistons fixedly connected to the valve slide are comparatively complicated and that only half the control pressure is available for the axial displacement of the valve slide into the working positions, so that the resolution is correspondingly low.
Dem gegenüber liegt der Erfindung die Aufgabe zugrunde, ein Wegeventil sowie eine damit ausgeführte LS-Steueranordnung zu schaffen, die einfach und kompakt ausgeführt ist und eine exakte Verschiebung der Ventilschieber in vorbestimmte Arbeitspositionen ermöglicht.On the other hand, the invention has for its object to provide a directional control valve and a LS-control arrangement designed therewith, which is designed to be simple and compact and allows an accurate displacement of the valve spool in predetermined working positions.
Diese Aufgabe wird hinsichtlich des Wegeventils durch die Merkmale des Patentanspruchs 1 und hinsichtlich der LS-Steueranordnung durch die Merkmale des Patentanspruchs 9 gelöst.This object is achieved with regard to the directional control valve by the features of patent claim 1 and with respect to the LS control arrangement by the features of claim 9.
Erfindungsgemäß ist das Wegeventil mit zwei koaxial zueinander angeordneten Ventilschiebern ausgebildet, die direkt, d. h. , ohne Zwischenschaltung einer Feder oder einer Zugstange oder dergleichen miteinander in Anlage bringbar sind. Die benachbarten Stirnflächen der Ventilschieber lassen sich mit dem gleichen Steuerdruck wie rückwärtige Steuerflächen beaufschlagen, deren Wirkfläche jedoch kleiner als diejenige der Stirnflächen ist. Durch Anlegen dieses Steuerdrucks können die beiden Ventil- - A -According to the directional valve is formed with two coaxially arranged valve spools, which are directly, ie, without the interposition of a spring or a tie rod or the like in abutment with each other. The adjacent end faces of the valve slide can be acted upon with the same control pressure as rear control surfaces, the effective area, however, is smaller than that of the end faces. By applying this control pressure, the two valve - A -
schieber entsprechend auseinander gefahren werden, um sehr schnell und exakt eine vorbestimmte Schieberstellung, beispielsweise eine Schwimmstellung einzunehmen. Dementsprechend sind bei der erfindungsgemäßen Lösung weder direkt am Ventilschieber angreifende elektrische Komponenten (beispielsweise Stößel eines Elektromagnets) zur Verschiebung erforderlich, noch muss zwischen den beiden Ventilschiebern ein Bauelement vorgesehen werden, um den Hub zu begrenzen. Die Verstellung in die vorbestimmte Schieberposition erfolgt aufgrund der Flächendifferenz, wobei die Stirnflächen und die Steuerflächen mit dem gleichen Steuerdruck beaufschlagt sind, so dass die Kanalführung gegenüber den herkömmlichen Lösungen wesentlich vereinfacht ist.slide appropriately driven apart to very quickly and accurately take a predetermined slide position, for example, a floating position. Accordingly, in the solution according to the invention neither directly on the valve spool engaging electrical components (such as plunger of an electromagnet) required for the shift, nor must a component be provided between the two valve spools to limit the stroke. The adjustment in the predetermined slide position is due to the area difference, wherein the end faces and the control surfaces are acted upon by the same control pressure, so that the channel guide over the conventional solutions is substantially simplified.
Bei einem Ausführungsbeispiel wird diese Flächendifferenz durch Kölbchen ausgebildet, die in die rückwärtigen Endabschnitte der Ventilschieber eintauchen und die sich am Gehäuse abstützen. Diese Kölbchen begrenzten mit dem jeweiligen Ventilschieber einen Kolbenraum, der mit dem Steuerdruck beaufschlagt ist.In one embodiment, this surface difference is formed by flasks that dip into the rear end portions of the valve spool and which are supported on the housing. These flasks limited with the respective valve spool a piston chamber which is acted upon by the control pressure.
Bei einem alternativen Ausführungsbeispiel werden in kinematischer Umkehr zur Bildung der Flächendifferenz die Endabschnitte der Ventilschieber radial zurückgesetzt und tauchen jeweils in eine Kappe ein, wobei die Zapfenstirnflächen die Steuerflächen mit verringertem Querschnitt bilden. Eine derartige Konstruktion ist per se aus der DE 3732445 Al (Fig. 5) bekannt.In an alternative embodiment, in kinematic reversal to form the area difference, the end portions of the valve spools are radially recessed and each dive into a cap, with the spigot faces forming the control surfaces of reduced cross-section. Such a construction is known per se from DE 3732445 A1 (FIG. 5).
Die Vorspannung der beiden Ventilschieber in ihre Grundposition erfolgt beispielsweise über zwei jeweils in einem Federraum aufgenommene Zentrierfedern, die jeweils an einem rückwärtigen Endabschnitt der Ventilschieber angreifen. Der die Zentrierfeder aufnehmende Federraum ist tankdruckbeaufschlagt . Jeder vom Ventilschieber und Kölbchen begrenzte Kolbenraum ist vorzugsweise über zumindest einen Manteldurchbruch, mit einem den Steuerdruck führenden Steuerraum der Ventilbohrung verbunden und nach einer Verschiebung mit Tankdruck beaufschlagbar.The bias of the two valve spool in its basic position, for example, via two each received in a spring chamber centering springs, which engage in each case at a rear end portion of the valve spool. The spring chamber accommodating the centering spring is subjected to tank pressure. Everyone from the valve spool and Kolbchen limited piston chamber is preferably connected via at least one shell breakthrough, leading to a control pressure control chamber of the valve bore and acted upon by a shift with tank pressure.
Der Aufbau des Wegeventils ist besonders einfach, wenn dieser Manteldurchbruch nach der Verschiebung der Ventilschieber den Kolbenraum mit dem Federraum verbindet.The structure of the directional control valve is particularly simple when this shell breakthrough connects the piston chamber with the spring chamber after the displacement of the valve spool.
Erfindungsgemäß wird es bevorzugt, wenn in der Ventilbohrung zwei den Tank- oder Rücklaufdruck führende Tankkammern außenliegend angeordnet sind, so dass zwei mit einem Druckanschluss verbundene Druckkammern, sowie zwei mit jeweils einem Arbeitsanschluss verbundene Arbeitskammern und eine zentrale, mit dem Steuerdruck beaufschlagte ZentralSteuerkammer sowie ggf. weitere Steuerkammern zwischen den Tankkammern angeordnet sind.According to the invention, it is preferred if two tank chambers leading to the tank or return pressure are arranged on the outside in the valve bore, so that two pressure chambers connected to a pressure connection and two working chambers connected to one working connection and a central central control chamber acted upon by the control pressure and optionally further control chambers are arranged between the tank chambers.
Der Zentralsteuerraum ist in der Grundposition über ein inverses Wechselventil mit den Kolbenräumen der Ventilschieber verbunden, so dass im Zentralsteuerraum stets der niedrigere der Steuerdrücke anliegt.The central control chamber is connected in the basic position via an inverse shuttle valve with the piston chambers of the valve spool, so that in the central control chamber always the lower of the control pressures is applied.
Die hydraulische Ansteuerung des Wegeventils erfolgt vorzugsweise durch zwei proportional wirkende Druckreduzierventile, über die die Steuerflächen der beiden Ventilschieber mit dem Steuerdruck beaufschlagbar sind und die in ihrer Grundstellung die Steuerflächen mit Tankdruck verbinden und somit entlasten.The hydraulic control of the directional control valve is preferably carried out by two proportionally acting pressure reducing valves, via which the control surfaces of the two valve spool can be acted upon by the control pressure and connect the control surfaces in their basic position with tank pressure and thus relieve.
Die LS-Steueranordnung wird vorzugsweise mit einer Individualdruckwaage ausgeführt und zumindest einem Arbeitsanschluss ein Sperrblock zugeordnet. Sonstige vorteilhafte Weiterbildungen der Erfindung sind Gegenstand weiterer Unteransprüche .The LS control arrangement is preferably carried out with an individual pressure compensator and at least one work connection assigned a blocking block. Other advantageous developments of the invention are the subject of further subclaims.
Im folgenden werden bevorzugte Ausführungsbeispiele der Erfindung anhand schematischer Zeichnungen näher erläutert. Es zeigen:In the following preferred embodiments of the invention will be explained in more detail with reference to schematic drawings. Show it:
Fig. 1 ein Schaltschema einer erfindungsgemäßen LS-1 is a circuit diagram of an inventive LS
5teueranordnung;5teueranordnung;
Fig. 2 eine konkrete Ausführung der LS-Steueranordnung gemäß Fig. 1 in Neutralstellung;FIG. 2 shows a concrete embodiment of the LS control arrangement according to FIG. 1 in the neutral position; FIG.
Fig. 3 eine vergrößerte Darstellung der Ventilschieber des Wegeventils aus Fig. 2;Fig. 3 is an enlarged view of the valve spool of the directional control valve of Fig. 2;
Fig. 4 die Ausführung gemäß Fig. 2 in einer Arbeitsstellung;FIG. 4 shows the embodiment according to FIG. 2 in a working position; FIG.
Fig. 5 die Ausführung gemäß Fig. 2 in einer Schwimmstellung undFig. 5 shows the embodiment of FIG. 2 in a floating position and
Fig. 6 ein weiteres konkretes Ausführungsbeispiel einer erfindungsgemäßen LS-Steueranordnung.Fig. 6 shows a further concrete embodiment of an LS control arrangement according to the invention.
Fig. 1 zeigt ein Schaltschema einer Ventilscheibe eines LS-Mobilsteuerblocks, über den hydraulische Verbraucher eines Traktors ansteuerbar sind. Die Ventilscheibe 1 hat zwei Arbeitsanschlüsse A, B, die beispielsweise zu den beiden Druckkammern eines Hydraulikzylinders führen, einen Druckanschluss P, zwei Ablauf- oder Tankanschlüsse Rl und R2, einen LS-Anschluss LS, einen Steuerdruckan- schluss Px sowie einen Steuerrücklaufanschluss Rx. Der Grundaufbau derartiger LS-Steueranordnungen bei Anwendungen in der Mobilhydraulik ist im Wesentlichen gleich, sie enthalten ein proportional verstellbares Wegeventil 2, das einen Geschwindigkeitsteil und einen Richtungsteil zur Einstellung des Druckmittelvolumenstroms zum bzw. vom Verbraucher enthält. Bei dem dargestellten Ausführungsbeispiel ist das Wegeventil 2 mit zwei Ventilschiebern 4,1 shows a circuit diagram of a valve disk of a LS mobile control block, via which hydraulic consumers of a tractor can be controlled. The valve disk 1 has two working ports A, B, which lead, for example, to the two pressure chambers of a hydraulic cylinder, a pressure port P, two drain or tank ports Rl and R2, an LS port LS, a control pressure port Px and a tax return port Rx. The basic structure of such LS control arrangements in applications in mobile hydraulics is essentially the same, they include a proportionally adjustable directional control valve 2, which contains a speed part and a direction part for adjusting the pressure medium volume flow to or from the consumer. In the illustrated embodiment, the directional control valve 2 with two valve spools 4,
6 ausgeführt, die in einer gemeinsamen Ventilbohrung koaxial zueinander aufgenommen sind und über eine Zentrierfederanordnung mit einer rechten Zentrierfeder 8 und einer linken Zentrierfeder 10 in die dargestellte Grundposition vorgespannt sind, in der die beiden Ventilschieber 4, 6 stirnseitig aneinander anliegen. Die Betätigung der Ventilschieberanordnung erfolgt über zwei elektrisch betätigbare Druckreduzierventile 12, 14, deren Eingangs- anschluss P mit dem Steuerdruckanschluss Px, an dem ein relativ hoher EingangsSteuerdruck anliegt und deren Tankanschluss T mit dem Steuerrücklaufanschluss Rx verbunden ist. Der Ausgangsanschluss A der Druckreduzierventile 12, 14 ist mit der Steuerseite des jeweils zugeordneten Ventilschiebers 4 bzw. 6 verbunden.6 performed in a common valve bore Coaxially with each other are received and are biased via a Zentrierfederanordnung with a right centering spring 8 and a left centering spring 10 in the illustrated basic position in which the two valve spool 4, 6 abut each other frontally. The actuation of the valve slide assembly via two electrically actuated pressure reducing valves 12, 14, whose input port P to the control pressure port Px, at which a relatively high input control pressure is applied and whose tank port T is connected to the control return port Rx. The output port A of the pressure reducing valves 12, 14 is connected to the control side of the respective associated valve spool 4 and 6 respectively.
Der Geschwindigkeitsteil des Wegeventils 2 wird jeweils durch eine durch Steuerkanten der Ventilschieber 4, 6 gebildete Zumessblenden 16, 18 gebildet, denen eine Individualdruckwaage 20 vorgeschaltet ist. Diese ist im Sinne einer Vergrößerung des Öffnungsquerschnitts durch die Kraft einer Druckwaagenfeder 22 und dem Lastdruck des zugeordneten Verbrauchers beaufschlagt, der über einen LS-Kanal 26 an der in Öffnungsrichtung wirksamen Steuerfläche der Druckwaage 20 anliegt. Der Lastdruck der über die anderen VentilScheiben des LS-Mobildrucks angesteuerten Verbraucher wird über den Steueranschluss Y^ an den Eingang eines Wechselventils 24 angelegt und mit dem Lastdruck des an die Ventilscheibe angeschlossenen Verbrauchers verglichen, der größte Lastdruck wird dann am LS-Anschluss abgegriffen. Bei dem dargestellten Ausführungsbeispiel wird der größere der Lastdrücke an den Arbeitsanschlüssen A, B über ein weiteres Wechselventil 28 abgegriffen, an dessen Ausgang der LS-Kanal 26 angeschlossen ist. In Schließrichtung ist die Druckwaage 20 von dem Druck im Druckmittelströmungspfad zwischen der Druckwaage 20 und dem Wegeventil 2 beaufschlagt. Die Druckwaage 20 hält in ihrer Regelposition den Druckabfall über der eingestellten Zumessblende 16 lastdruckunabhän- gig konstant. Wie bei derartigen LS-Steueranordnungen üblich, wird der höchste Lastdruck aller vom Mobilsteuerblock angesteuerten Verbraucher zu einem Pumpenregler einer Verstellpumpe oder zur Bypassdruckwaage einer Konstantpumpe geführt, wodurch der Pumpendruck in einer Pumpenleitung so eingestellt wird, dass er stets um ein vorbestimmtes Δp oberhalb dieses maximalen Lastdrucks liegt.The speed part of the directional control valve 2 is formed in each case by an orifices 16, 18 formed by control edges of the valve spool 4, 6, to which an individual pressure compensator 20 is connected upstream. This is acted upon in the sense of an enlargement of the opening cross section by the force of a pressure compensator spring 22 and the load pressure of the associated consumer, which rests on an LS channel 26 at the effective in the opening direction control surface of the pressure compensator 20. The load pressure of the consumers driven via the other valve disks of the LS mobile pressure is applied via the control connection Y 1 to the input of a shuttle valve 24 and compared with the load pressure of the consumer connected to the valve disk, the largest load pressure is then tapped off at the LS connection. In the illustrated embodiment, the larger of the load pressures at the working ports A, B is tapped via another shuttle valve 28, at the output of the LS channel 26 is connected. In the closing direction, the pressure compensator 20 is acted upon by the pressure in the pressure medium flow path between the pressure compensator 20 and the directional control valve 2. The pressure compensator 20 holds in its control position the pressure drop above the adjusted metering orifice 16, independent of load pressure, constant. As usual with such LS control arrangements, the highest load pressure of all controlled by the mobile control block consumer is led to a pump governor of a variable or bypass pressure compensator of a constant pump, whereby the pump pressure in a pump line is adjusted so that it always by a predetermined Δp above this maximum load pressure lies.
Zum Einstellen einer Schwimmstellung können die beiden Ventilschieber 4, 6 aus der dargestellten Grundposition gegen die Kraft der Zentrierfedern 8 , 10 nach außen bewegt werden. Dazu ragen die aufeinander zuweisenden Stirnflächen der Ventilschieber 4, 6 in eine gemeinsame Zentraldruckkammer 30, die mit dem Ausgangsdruck der Druckreduzierventile 12 oder 14 beaufschlagbar ist. Für den Fall, dass diese Druckreduzierventile 12, 14 auf unterschiedliche Steuerdrücke eingestellt sind, wird über ein inverses Wechselventil 32 der kleinere dieser Steuerdrücke abgegriffen und zu der an den Ausgang dieses inversen Wechselventils 32 angeschlossenen Zentralsteuerdruckkammer 30 weitergeleitet. Wenn beide Druckreduzierventile 12, 14 auf den gleichen Steuerdruck eingestellt sind, liegt dieser Steuerdruck auch in der Zentralsteuerdruckkammer 30 an.To set a floating position, the two valve slides 4, 6 can be moved out of the illustrated basic position against the force of the centering springs 8, 10 to the outside. For this purpose, the mutually facing end faces of the valve slide 4, 6 project into a common central pressure chamber 30, which is acted upon by the output pressure of the pressure reducing valves 12 or 14. In the event that these pressure reducing valves 12, 14 are set to different control pressures, the smaller of these control pressures is tapped via an inverse shuttle valve 32 and forwarded to the central control pressure chamber 30 connected to the output of this inverse shuttle valve 32. If both pressure reducing valves 12, 14 are set to the same control pressure, this control pressure is also present in the central control pressure chamber 30.
Im Druckmittelstrδmungspfad zwischen dem Wegeventil und dem zugeordneten Arbeitsanschlüssen A, B ist jeweils ein Sperrblock 34, 36 vorgesehen, deren Aufbau anhand Fig. 2 näher erläutert ist. Derartige Sperrblöcke 34, 36 lassen eine Druckmittelströmung zum zugeordneten Arbeits- anschluss A, B zu. Um eine Druckmittelrückströmung vom Verbraucher zu ermöglichen, kann der Sperrblock 34, 36 mittels eines Aufstoßkolbens entriegelt werden. Bei ziehenden Lasten wirkt dieser Sperrblock 34, 36 dann als Druckwaage, die es ermöglicht mit der über das Wegeventil aufgesteuerten Ablaufmessblende 38, 40 eine lastdruckun- abhängige Druckmittelsteuerung durchzuführen. Über das weitere Wechselventil 28 wird im Falle einer ziehenden Last der dann größere Druck auf der Ablaufseite abgegriffen und in den LS-Kanal 26 gemeldet, so dass eine hinreichende Druckmittelversorgung auch im Falle einer ziehenden Last gewährleistet ist und Kavitationen verhindert werden können. Weitere Einzelheiten hierzu können der DE 103 21 914 Al der Anmelderin entnommen werden.In the pressure medium flow path between the directional control valve and the associated working ports A, B is in each case a blocking block 34, 36 is provided, whose structure is explained in more detail with reference to FIG. Such blocking blocks 34, 36 allow a flow of pressure medium to the associated working port A, B. In order to allow a pressure medium backflow from the consumer, the locking block 34, 36 can be unlocked by means of a poppet piston. When pulling loads this lock block 34, 36 then acts as Pressure compensator, which makes it possible to carry out a load pressure-independent pressure medium control with the drain metering orifice 38, 40 controlled via the directional control valve. About the additional shuttle valve 28, the greater pressure on the discharge side is then tapped and reported in the LS channel 26 in the case of a towing load, so that a sufficient pressure medium supply is ensured even in the case of a towing load and cavitations can be prevented. Further details can be found in DE 103 21 914 A1 of the applicant.
Der Verlauf der in Fig. 1 dargestellten Steuer- und Druckmittelkanäle wird anhand des konkreten Ausführungs- beispiels in Fig. 2 erläutert.The course of the control and pressure medium channels shown in Fig. 1 will be explained with reference to the concrete embodiment in Fig. 2.
Fig. 2 zeigt eine konkrete Ausführungsform der Ventilscheibe 1 eines Mobilsteuerblocks. Diese Ventilscheibe 1 wird in Querrichtung von einer Ventilbohrung 42 durchsetzt, in der die beiden Ventilschieber 4, 6 axial verschiebbar geführt sind. Die beiden Ventilschieber werden über die Zentrierfedern 8, 10 in eine Anlageposition vorgespannt, in der die Stirnflächen 44, 46 der Ventil- Schieber 4, 6 aneinander anliegen. Die Zentrierfedern 8, 10 sind an die Ventilbohrung 42 axial abschließenden Federkappen 48, 50 abgestützt, die jeweils einen Federraum begrenzen, in dem stets der Tank- oder Rücklaufdruck anliegt, der über den in Fig. 2 an den Federraum angrenzenden, nur im Querschnitt dargestellten Kanal abgegriffen wird.Fig. 2 shows a concrete embodiment of the valve disc 1 of a mobile control block. This valve disk 1 is traversed in the transverse direction by a valve bore 42, in which the two valve spools 4, 6 are guided axially displaceably. The two valve slides are biased via the centering springs 8, 10 in an abutment position in which the end faces 44, 46 of the valve slide 4, 6 abut each other. The centering springs 8, 10 are supported on the valve bore 42 axially final spring caps 48, 50, each delimiting a spring chamber in which always the tank or return pressure is applied, the above the in Fig. 2 adjacent to the spring chamber, shown only in cross section Channel is tapped.
In jedem in den Federraum eintauchenden Endabschnitt der Ventilschieber 4, 6 ist ein Kolbenraum 52 bzw. 54 ausgebildet, wobei der Kolbenraum des Ventilschiebers 6 lediglich gestrichelt angedeutet ist. In die Kolbenräume 52, 54 ist jeweils ein Kölbchen 56, 58 eingesetzt, die mit einem aus dem Ventilschieber 4 , 6 hervorstehenden Endabschnitt an dem Boden der Federkappe 48 bzw. 50 abgestützt sind. Die Kölbchen 56, 58 schließen die beiden Kolbenräume 52, 54 in Axialrichtung druckmitteldicht ab. Die Bodenflächen jedes Kolbenraums 52, 54 bilden jeweils eine Steuerfläche 60, 62 deren Wirkfläche geringer ist als die Querschnittsfläche der Stirnfläche 44, 46 des jeweiligen Ventilschiebers 4 bzw. 6. In die beiden Kolbenräume 52, 54 münden jeweils axial beabstandete Mantelbohrungen 64, 66 bzw. 68, 70 ein, auf deren Funktion noch im Folgenden eingegangen wird. Anstelle dieser Mantelbohrungen 64, 66; 67, 70 könnte jeweils auch ein Langloch vorgesehen werden. Sie sollen von den Kölbchen 56, 58 nicht überdeckt werden.In each plunging into the spring chamber end portion of the valve slide 4, 6, a piston chamber 52 and 54 is formed, wherein the piston chamber of the valve spool 6 is indicated only by dashed lines. In the piston chambers 52, 54 each have a piston 56, 58 is inserted, the are supported with a protruding from the valve spool 4, 6 end portion at the bottom of the spring cap 48 and 50 respectively. The flasks 56, 58 close the two piston chambers 52, 54 in the axial direction pressure medium-tight. The bottom surfaces of each piston chamber 52, 54 each form a control surface 60, 62 whose effective area is less than the cross-sectional area of the end face 44, 46 of the respective valve slide 4 and 6. In the two piston chambers 52, 54 open respectively axially spaced shell bores 64, 66 and 68, 70, the function of which will be discussed below. Instead of these jacket bores 64, 66; 67, 70, a slot could be provided in each case. They should not be covered by the flasks 56, 58.
Anstelle durch die Kölbchen 56, 58 können die mit geringerer Wirkflächen ausgeführten Steuerflächen 60, 62 in kinematischer Umkehr auch gebildet werden, in dem die Endabschnitte der Ventilschieber 4, 6 zapfenförmig zurückgestuft und in Kappen eintauchen, so dass durch jeweils eine Kappe und einen Endabschnitt ein von der Steuerfläche 60, 62 begrenzter Raum gebildet ist, der über Kanäle in Ventilschieber 4, 6 mit dem Steuerdruck oder mit Tankdruck beaufschlagbar ist.Instead of the flasks 56, 58, the control surfaces 60, 62 designed with lower effective surfaces can also be formed in kinematic reversal, in which the end sections of the valve spools 4, 6 are recessed in the form of pegs and immersed in caps, so that a respective cap and an end section is formed by the control surface 60, 62 limited space, which can be acted upon by channels in the valve slide 4, 6 with the control pressure or tank pressure.
In der Ventilbohrung sind in der Darstellung gemäß den Figuren 2 und 3 von außen nach innen zwei außenliegende Tankkammern 72, 74, zwei Arbeitskammern 76, 78, zwei Zulaufkammern 80, 82, zwei Steuerdruckkammern 84, 86, zwei innen davon angeordnete Steuerkammern 88, 90 und die mittige ZentralSteuerkammer 92 ausgebildet. Die beiden Tankkammern 72, 74 sind über nicht dargestellte Kanäle mit den Federräumen und den beiden Rücklaufanschlüssen Rl, R2 (Fig. 1) der Ventilscheibe 1 verbunden. Die beiden innen davon angeordneten Arbeitskammern 76, 78 führen über einen Vorlaufkanal 94 zum Arbeitsanschluss A bzw. über einen Rücklaufkanal 96 zum Arbeitsanschluss B. Die beiden Zulaufkammern 80, 82 sind über einen Zulaufkanal 98 miteinander verbunden, in den der Ausgang der Individualdruckwaage 20 einmündet, deren Eingang über eine Druckwaageneingangskammer 100 mit dem Druckanschluss P (Fig. 1) der Ventilscheibe 1 verbunden ist. Ein die Druckwaagenfeder 22 aufnehmender Federraum 102 der Druckwaage 20 ist über den LS-Kanal 26 an den Ausgang des Wechselventils 24 angeschlossen und weiter zum Ausgang des weiteren Wechselventils 28 geführt, dessen beiden Eingänge über einen etwa U-förmigen Verbindungskanal 104 mit der Arbeitskammer 76 bzw. 78 verbunden sind.In the valve bore, in the representation according to FIGS. 2 and 3, two external tank chambers 72, 74, two working chambers 76, 78, two inlet chambers 80, 82, two control pressure chambers 84, 86, two control chambers 88, 90 arranged inside thereof and the central central control chamber 92 is formed. The two tank chambers 72, 74 are connected via channels, not shown, with the spring chambers and the two return connections Rl, R2 (FIG. 1) of the valve disk 1. The two inside arranged working chambers 76, 78 lead via a flow channel 94 to the working port A. or via a return channel 96 to the working port B. The two inlet chambers 80, 82 are connected to each other via an inlet channel 98 into which the output of the individual pressure compensator 20 opens, the input via a pressure compensator input chamber 100 to the pressure port P (Fig 1 is connected. A compression chamber spring 22 receiving spring chamber 102 of the pressure compensator 20 is connected via the LS channel 26 to the output of the shuttle valve 24 and further guided to the output of the further shuttle valve 28, the two inputs via an approximately U-shaped connecting channel 104 with the working chamber 76 and 78 are connected.
Wie in Fig. 2 angedeutet, sind die Eingangsanschlüsse P der beiden Druckreduzierventile 12, 14 mit dem Steuer- druckanschluss Px und deren Tankanschlüsse T mit Steuerrücklaufanschluss Rx verbunden. Die beiden Ausgangsanschlüsse A sind über Vorsteuerkanäle 106, 108 zu den Eingängen des inversen Wechselventils 32 geführt, dessen Ausgang mit der ZentralSteuerkammer 92 verbunden ist.As indicated in FIG. 2, the input ports P of the two pressure reducing valves 12, 14 are connected to the control pressure port Px and their tank ports T are connected to the control return port Rx. The two output ports A are fed via pilot control channels 106, 108 to the inputs of the inverse shuttle valve 32, the output of which is connected to the central control chamber 92.
Wie insbesondere der vergrößerten Darstellung der beiden Ventilschieber 4, 6 gemäß Fig. 3 entnehmbar ist, sind an diesen von außen nach innen Tanksteuerkanten 110, 112, Zulaufsteuerkanten 114, 116, Steuerkanten 118, 120 sowie weitere Steuerkanten 158, 159 ausgebildet, die jeweils von Umfangskanten eines Kolbenbundes gebildet sind. Wie weiter Fig. 3 entnehmbar ist, münden die Mantelbohrungen 64, 68 in den Vorsteuerkanal 106 bzw. 108 ein, die beiden anderen Mantelbohrungen 66, 70 sind in der Grundposition überdeckt.As in particular the enlarged view of the two valve spool 4, 6 as shown in FIG. 3 can be removed, are formed on these from the outside to the inside tank control edges 110, 112, inlet control edges 114, 116, control edges 118, 120 and further control edges 158, 159, each of Peripheral edges of a piston collar are formed. As further Fig. 3 can be removed, open the jacket holes 64, 68 in the pilot channel 106 and 108, the two other shell bores 66, 70 are covered in the basic position.
Die beiden Sperrblöcke 34, 36 sind gemäß Fig. 2 in den Vorlaufkanal 94 bzw. den Rücklaufkanal 96 eingesetzt. Sie haben einen mit einer Vorsteueröffnung ausgeführten Schließkörper 122 bzw. 124, der jeweils von einer Schließfeder 126, 128 gegen einen Ventilsitz 130, 132 vorgespannt ist. In jedem Ventilkörper 122, 124 ist ein Vorsteuerventilkörper 134, 136 aufgenommen und gegen einen weiteren Vorsteuerventilsitz vorgespannt. Jeder Vorsteuerventilkörper 134, 136 lässt sich mittels eines Aufstoßkolbens 138, 140 von seinem Vorsteuerventilsitz abheben, indem an seine Kolbenfläche 142, 144 ein Steuerdruck angelegt ist. Dazu begrenzt die Kolbenfläche 142, 144 einen Druckraum, der über Steuerkanalabschnitte 146, 148 mit den beiden Steuerkammern 88, 90 verbunden ist, die über die weiteren Steuerkanten 158, 159 mit der ZentralSteuerkammer 92 verbunden sind. Ein Federraum 150, 152 des Sperrblocks 34, 36 ist über einen kurzen Kanalabschnitt mit dem Vorsteuerkanal 106, 108 verbunden. Der Federraum 150, 152 ist des Weiteren mit dem Arbeitsan- schluss A, B verbunden.The two blocking blocks 34, 36 are inserted as shown in FIG. 2 in the flow channel 94 and the return channel 96. You have a running with a pilot opening closing body 122 and 124, each of a Closing spring 126, 128 is biased against a valve seat 130, 132. In each valve body 122, 124, a pilot valve body 134, 136 is received and biased against another pilot valve seat. Each pilot valve body 134, 136 can be lifted off its pilot valve seat by means of a poppet piston 138, 140 by applying a control pressure to its piston surface 142, 144. For this purpose, the piston surface 142, 144 limits a pressure chamber, which is connected via control channel sections 146, 148 to the two control chambers 88, 90, which are connected to the central control chamber 92 via the further control edges 158, 159. A spring chamber 150, 152 of the blocking block 34, 36 is connected to the pilot channel 106, 108 via a short channel section. The spring chamber 150, 152 is further connected to the working port A, B.
In der in den Figuren 1 bis 3 dargestellten Grundposition (Neutralstellung) des Wegeventils 2 strömt das Druckmittel über die Individualdruckwaage 20 zu und steht im Zulaufkanal 98 an. Die beiden Druckreduzierventile 12, 14 sind unbestromt, so dass die beiden Vorsteuerkanäle 106, 108 zum Rücklaufanschluss Rx hin entlastet sind. Entsprechend sind auch die beiden Kolbenflächen 142, 144 der Aufstoßkolben 138, 140 zum Rücklaufanschluss Rx hin entlastet . Die beiden Schieber 4 , 6 nehmen aufgrund der Vorspannung der Zentrierfedern 8, 10 ihre dargestellte Mittelposition ein, in der die Steuerkanten 112, 114 und 116, 118 die Druckmittelverbindung der Arbeitsanschlüsse A, B zum Druckanschluss P und zu den Rücklaufanschlüssen Rl und R2 absperren. Die beiden Arbeitskammern 76, 78 und damit der Vorlaufkanal 94 und der Rücklaufkanal 96 sind jeweils über im Ventilschieber 4 bzw. 6 ausgebildete Verbindungsbohrungen 154, 156 (gestrichelt in den Figuren 2 und 3) mit den Tankkammern 72, 74 und damit mit den Rücklaufanschlüssen Rl und R2 verbunden und somit eben- falls druckentlastet. Das Lastdrucksignal, das über den Verbindungskanal 104 und das darin angeordnete weitere Wechselventil 28 abgegriffen wird, ist dann entsprechend für diese Ventilscheibe 1 ebenfalls auf Tankdruckniveau. Die beiden Sperrblöcke 34, 36 sind gesperrt, da die beiden Ventilkörper 122, 124 durch den jeweiligen Lastdruck und die Schließfedern 126, 128 gegen die zugeordneten Ventilsitze 130, 132 gedrückt sind.In the basic position (neutral position) of the directional control valve 2 illustrated in FIGS. 1 to 3, the pressure medium flows via the individual pressure compensator 20 and arrives in the inlet channel 98. The two pressure reducing valves 12, 14 are de-energized, so that the two pilot control channels 106, 108 are relieved to the return port Rx. Correspondingly, the two piston surfaces 142, 144 of the poppet pistons 138, 140 are also relieved to the return port Rx. The two slides 4, 6 take due to the bias of the centering springs 8, 10 their illustrated center position in which the control edges 112, 114 and 116, 118 shut off the pressure medium connection of the working ports A, B to the pressure port P and to the return ports Rl and R2. The two working chambers 76, 78 and thus the flow channel 94 and the return channel 96 are respectively formed in the valve slide 4 and 6 connecting bores 154, 156 (dashed lines in Figures 2 and 3) with the tank chambers 72, 74 and thus with the return ports Rl and R2, and thus if pressure relieved. The load pressure signal, which is tapped via the connecting channel 104 and arranged therein another shuttle valve 28 is then corresponding to this valve disc 1 also at tank pressure level. The two locking blocks 34, 36 are locked because the two valve bodies 122, 124 are pressed by the respective load pressure and the closing springs 126, 128 against the associated valve seats 130, 132.
Soll nun beispielsweise das Druckmittel über den Ar- beitsanschluss A zum Verbraucher und von diesem über den Arbeitsanschluss B zurückströmen, so wird das Druckreduzierventil 12 bestromt. Der Steuerdruck, der sich proportional zur Bestromung des Druckreduzierventils einstellt, wird über den Ausgangsanschluss A des Druckreduzierventils 12, den Vorsteuerkanal 108 und die Mantelbohrungen 70 und - nach einer AxialVerschiebung der Ventilschieber - 68 in den linken Kolbenraum 54 geführt. Der rechte Kolbenraum 52 ist - wie in der Neutralsteilung - noch über das unbestromte Druckreduzierventil 14 zum Rücklauf Rx hin entlastet. Entsprechend liegt auch im rechten Vorsteuerkanal 106 der Tankdruck an. Der über das Druckreduzierventil 12 eingestellte Steuerdruck liegt auch am linken Eingang des inversen Wechselventil 32 an, während an dessen rechten Eingang über den Vorsteuerkanal 106 der Tankdruck anliegt - das inverse Wechselventil 32 ist somit zum Tankdruck hin geöffnet, so dass dieser in der Zentralsteuerkammer 92 wirkt .If, for example, the pressure medium now flows back to the consumer via the working connection A and from this via the working connection B, the pressure reducing valve 12 is energized. The control pressure, which is proportional to the supply of the pressure reducing valve is guided via the output port A of the pressure reducing valve 12, the pilot passage 108 and the shell bores 70 and - after an axial displacement of the valve spool - 68 in the left piston chamber 54. The right piston chamber 52 is - as in the neutral division - still relieved via the no-load pressure reducing valve 14 to return R x out. Accordingly, the tank pressure is also present in the right pilot control channel 106. The set via the pressure reducing valve 12 control pressure is applied to the left input of the inverse shuttle valve 32, while at its right input via the pilot passage 106, the tank pressure is applied - the inverse shuttle valve 32 is thus opened to the tank pressure, so that it acts in the central control chamber 92 ,
Die beiden Ventilschieber 4, 6 werden durch den Druck auf die Steuerfläche 62 gemäß der Darstellung in Fig. 4 nach rechts verschoben, wobei sich das Kölbchen 58 weiter an der Federkappe 50 abstützt. Der Hub der Ventilschieber 4, 6 wird bestimmt durch den Durchmesser des Kölbchens 58, die Fläche der Steuerfläche 62, die Kraft der Zentrierfeder 8 und die Größe des vom Druckreduzierventil 12 eingestellten Steuerdrucks. Durch die Axialverschiebung nach rechts wird über die Zulaufsteuerkante 116 die Verbindung von der Zulaufkammer 82 zur Arbeitskammer 78 aufgesteuert, so dass das Druckmittel vom Ausgang der Druckwaage 20 in den Vorlaufkanal 94 einströmen kann. Der nun als Rückschlagventil wirkende Ventilkörper 124 wird von seinem Ventilsitz 132 abgehoben und der Druckmittelvolumenstrom zum Arbeitsanschluss A freigegeben. Die Kolbenfläche 144 des Aufstoßkolbens 140 ist dabei über die ZentralSteuerkammer 92 und das inverse Wechselventil 32 mit Tankdruck beaufschlagt. Über die weitere Steuerkante 158 des Ventilschiebers 4 wird die Verbindung der Steuerkammer 88 mit der druckentlasteten Zentralsteuerkammer 92 abgesperrt und über die Steuerkante 118 eine Verbindung mit der den Eingangssteuerdruck des Druckreduzierventils 12, 14 führenden Steuerdruckkammer 84 aufgesteuert, so dass die Kolbenfläche 42 des Aufstoßkolbens 138 mit dem hohen Eingangssteuerdruck des Druckreduzierventils 12 beaufschlagt ist. Der Aufstoßkolben 138 wird dadurch gemäß Fig. 4 nach rechts verschoben und hebt den Vorsteuerventilkörper 134 gegen die Kraft seiner Ventilfeder vom Vorsteuersitz ab, so dass der Druck im Federraum 150, der zuvor dem Lastdruck des Verbrauchers entsprach, abgebaut wird. Sobald dieser Druck im Federraum 150 soweit abgesunken ist, dass ein Kräftegleichgewicht vorliegt zwischen dem Druck im Federraum, der auf die federraumseitige Stirnfläche des Ventilkörpers 122 wirkt und dem Lastdruck, der auf die Differenzfläche wirkt, die aus dem Kolbendurchmesser des Ventilkörpers 122 und dem Durchmesser des Ventilsitzes 130 gebildet ist, folgt der Ventilkörper 122 dem Vorsteuerventilkörper 134 und das Druckmittel kann vom Verbraucher über den Arbeitsan- schluss B, den Rücklaufkanal 96 und die durch die Tanksteuerkante 110 aufgesteuerte Verbindung zwischen der Arbeitskammer 76 und der Tankkammer 72 zum Rücklaufan- schluss R2 abströmen. Der Druck, der an der Tanksteuer- kante 110 und damit im Rücklaufkanal 96 anliegt, wirkt auf den Aufstoßkolben 138 zurück, so dass dieser zusammen mit dem Ventilkörper 130 des Sperrblocks 34 wie eine Ablaufdruckwaage wirkt, die den Ablaufdruck an der Tanksteuerkante 110 des Ventilschiebers 4 konstant hält, und damit bei ziehenden Lasten eine lastdruckunabhängige Ablaufsteuerung ermöglicht. Die beiden Mantelbohrungen 64, 66 öffnen sich während der Axialverschiebung des Ventilschiebers 4 hin zum Federraum der Zentrierfeder 8, in dem ebenfalls Tankdruck anliegt.The two valve spool 4, 6 are moved by the pressure on the control surface 62 as shown in FIG. 4 to the right, wherein the piston 58 is further supported on the spring cap 50. The stroke of the valve slide 4, 6 is determined by the diameter of the piston 58, the surface of the control surface 62, the force of the centering spring 8 and the size of the pressure reducing valve 12th set control pressure. Due to the axial displacement to the right, the connection from the inlet chamber 82 to the working chamber 78 is opened via the inlet control edge 116 so that the pressure medium can flow from the outlet of the pressure compensator 20 into the inlet channel 94. The now acting as a check valve body 124 is lifted from its valve seat 132 and released the pressure medium flow to the working port A. The piston surface 144 of the poppet 140 is acted upon by the central control chamber 92 and the inverse shuttle valve 32 with tank pressure. About the further control edge 158 of the valve spool 4, the connection of the control chamber 88 is shut off with the pressure-relieved central control chamber 92 and via the control edge 118 opens a connection with the input control pressure of the pressure reducing valve 12, 14 leading control pressure chamber 84, so that the piston surface 42 of the poppet 138 with the high input control pressure of the pressure reducing valve 12 is acted upon. The poppet 138 is thereby moved to the right in FIG. 4 and lifts the pilot valve body 134 against the force of its valve spring from the pilot seat, so that the pressure in the spring chamber 150, which previously corresponded to the load pressure of the consumer, is reduced. Once this pressure in the spring chamber 150 has dropped so far that a balance of forces between the pressure in the spring chamber, which acts on the spring-side end face of the valve body 122 and the load pressure acting on the differential surface, from the piston diameter of the valve body 122 and the diameter of the Valve seat 130 is formed, the valve body 122 follows the pilot valve body 134 and the pressure medium can flow from the consumer via the working port B, the return channel 96 and the controlled by the tank control edge 110 connection between the working chamber 76 and the tank chamber 72 to the return port R2 , The pressure at the fuel tank Edge 110 and thus rests in the return channel 96, acts on the topping piston 138, so that this acts together with the valve body 130 of the locking block 34 as a discharge pressure compensator, which keeps the discharge pressure at the tank control edge 110 of the valve spool 4 constant, and thus pulling loads allows a load pressure independent flow control. The two jacket bores 64, 66 open during the axial displacement of the valve slide 4 towards the spring chamber of the centering spring 8, in which also tank pressure is applied.
Zur Einstellung der weiteren Arbeitsstellungen, in denen das Druckmittel über den Arbeitsanschluss B zum Verbraucher und über den Arbeitsanschluss A vom Verbraucher abströmt, wird entsprechend durch Bestromung des Druckreduzierventils 14 eingestellt.To set the other working positions in which the pressure fluid flows through the working port B to the consumer and the working port A from the consumer, is adjusted accordingly by energizing the pressure reducing valve 14.
Zur Einstellung der Schwimmstellung, in der die beiden Arbeitsanschlüsse A, B beide mit dem Rücklaufan- schluss R1/R2 verbunden sind und der Druckanschluss P abgesperrt ist, werden beide Druckreduzierventile 12, 14 bestromt, so dass an deren Ausgängen A der gleiche Ausgangssteuerdruck eingestellt wird. Dieser Ausgangssteuerdruck der beiden Druckreduzierventile 12, 14 liegt dann über die Vorsteuerkanäle 106, 108 auch an den beiden Eingängen des inversen Wechelventils 32 sowie an den Steuerflächen 60, 62 der Kolbenräume 52, 54 (siehe Fig. 2) an. Da an beiden Eingängen des inversen Wechselventils 32 der gleiche Ausgangssteuerdruck anliegt, wird auch die Zentralsteuerkammer 92 mit diesem Druck beaufschlagt. Da die an die Zentralsteuerkammer 92 angrenzenden Stirnflächen 44, 46 der Ventilschieber 4, 6 größer sind als die Steuerflächen 60, 62 der Kolbenräume 52, 54 (in Fig. 5 nur 52, 60 dargestellt) werden die beiden Ventilschieber 4, 6 gegen die Kraft der vergleichsweise schwachen Zentrierfedern 8, 10 auseinanderbewegt. Dabei wird über die Steuerkanten 118, 120 die Verbindung der Steuerkämmern 88, 90 zu den Steuerdruckkammern 84, 86 aufgesteuert, so dass die Kolbenflächen 142, 144 der beiden AufstoßkolbenTo set the floating position, in which the two working ports A, B are both connected to the return port R1 / R2 and the pressure port P is shut off, both pressure reducing valves 12, 14 are energized, so that at their outputs A, the same output control pressure is set , This output control pressure of the two pressure reducing valves 12, 14 is then via the pilot control channels 106, 108 also at the two inputs of the inverse exchange valve 32 and to the control surfaces 60, 62 of the piston chambers 52, 54 (see FIG. 2). Since the same output control pressure is present at both inputs of the inverse shuttle valve 32, the central control chamber 92 is also subjected to this pressure. Since the end surfaces 44, 46 of the valve spools 4, 6 adjoining the central control chamber 92 are larger than the control surfaces 60, 62 of the piston chambers 52, 54 (only 52, 60 shown in FIG. 5), the two valve spools 4, 6 are against the force the comparatively weak centering springs 8, 10 moved apart. It is about the Control edges 118, 120, the connection of the Steuerkämmern 88, 90 controlled to the control pressure chambers 84, 86, so that the piston surfaces 142, 144 of the two Aufstoßkolben
138, 140 mit dem hohen Steuereingangsdruck am Steueran- schluss Px beaufschlagt sind. Beide Sperrventile 34, 35 werden - wie vorstehend im Zusammenhang in Fig. 4 - geöffnet und somit die beiden Arbeitsanschlüsse A, B über den Vorlaufkanal 94, den Rücklaufkanal 96, die beiden Arbeitskammern 76, 78, die Tanksteuerkanten 110, 112 und die außenliegenden Tankkammern 72, 74 mit den Rücklaufan- schlüssen R1/R2 verbunden. Die Zulaufsteuerkanten 114, 116 sperren die Verbindung zum Zulaufkanal 98 und damit zum Ausgang der Druckwaage 20 ab - die Schwimmstellung ist eingestellt.138, 140 are acted upon by the high control input pressure at the control connection P x . Both check valves 34, 35 are - as in the context in Fig. 4 - opened and thus the two working ports A, B via the flow channel 94, the return channel 96, the two working chambers 76, 78, the tank control edges 110, 112 and the outer tank chambers 72, 74 connected to the return ports R1 / R2. The inlet control edges 114, 116 block the connection to the inlet channel 98 and thus to the output of the pressure compensator 20 - the floating position is set.
Wie des Weiteren Fig. 5 entnehmbar ist, öffnen die beiden Mantelbohrungen 64, 66 des Ventilschiebers 4 und 68, 70 des Ventilschiebers 6 die Verbindung zwischen dem Federraum der Zentrierfeder 8 bzw. 10 mit dem jeweiligen Kolbenraum 52, 54 (letzterer nicht dargestellt in Fig. 5) , so dass die Steuerflächen 60, 62 (siehe Fig. 2) nicht mehr wie zuvor von dem über die Druckreduzierventile 12,5, the two casing bores 64, 66 of the valve slide 4 and 68, 70 of the valve slide 6 open the connection between the spring chamber of the centering spring 8 and 10 with the respective piston chamber 52, 54 (the latter not shown in FIG 5), so that the control surfaces 60, 62 (see FIG. 2) no longer, as before, from the one via the pressure reducing valves 12,
14 eingestellten Steuerdruck, sondern von dem in den Federräumen anliegenden Tankdruck beaufschlagt sind. Da die beiden Stirnflächen 44, 46 wesentlich größer als die Steuerflächen 60, 62 sind und diese druckentlastet werden, können die Druckreduzierventile 12, 14 auf einen wesentlich geringeren Ausgangsdruck eingestellt werden, um die Ventilschieber 4, 6 über längere Zeit gegen die Kraft der Zentrierfedern 8, 10 in ihrer Schwimmstellung zu halten.14 set control pressure, but are acted upon by the voltage applied in the spring chambers tank pressure. Since the two end faces 44, 46 are substantially larger than the control surfaces 60, 62 and these are depressurized, the pressure reducing valves 12, 14 can be set to a much lower output pressure to the valve spool 4, 6 for a long time against the force of the centering springs. 8 To keep 10 in their floating position.
Wie dem Ausführungsbeispiel gemäß Fig. 6 entnehmbar, kann die LS-Steueranordnung mit nur einem Sperrblock 34 ausgebildet werden, wobei die Kanalführung im Wesentlichen dem vorbeschriebenen Ausführungsbeispiel entspricht, mit der Ausnahme, dass nunmehr der Verbindungskanal 104, über den der Lastdruck abgegriffen wird nicht mehr zur Arbeitskammer 78 sondern zu einer Kammer 160 führt, die in der dargestellten Grundposition über die etwas länger als bei den vorher beschriebenen Ausführungsbeispielen ausgeführte Verbindungsbohrung 156 mit der linken Tankkammer 74 verbunden ist. Bei der Axialverschiebung des Ventilschiebers 6 nach rechts wird dann über eine Zusatz- steuerkante 162 die Verbindung zur Steuerkammer 90 aufgesteuert, über die dann der Lastdruck am Arbeitsanschluss A in den Verbindungskanal 104 gemeldet wird. Das heißt, die Kammern am Ventilschieber 4, 6, die bei der Verwendung von Sperrblöcken zum Steuern des Aufstoßdruckes dienen, werden bei diesem Ausführungsbeispiel zum Abgriff des Lastdrucks verwendet. Bei dem Ausführungsbeispiel gemäß Fig. 6 sind entsprechend die beiden Ventilschieber 4, 6 nicht mehr identisch ausgebildet.As can be seen from the exemplary embodiment according to FIG. 6, the LS control arrangement can be formed with only one blocking block 34, the channel guidance substantially corresponding to the above-described embodiment, with the exception that now the connecting channel 104, via which the load pressure is tapped no longer leads to the working chamber 78 but to a chamber 160 which in the illustrated basic position on the slightly longer than in the previously described embodiments executed connecting bore 156 with the left tank chamber 74 is connected. During the axial displacement of the valve slide 6 to the right, the connection to the control chamber 90 is then opened via an additional control edge 162, via which the load pressure at the working connection A is then reported to the connection channel 104. That is, the chambers on the valve spool 4, 6, which serve in the use of blocking blocks for controlling the impact pressure, are used in this embodiment for tapping off the load pressure. In the embodiment according to FIG. 6, the two valve slides 4, 6 are correspondingly no longer identical.
Prinzipiell können auch beide Sperrventile und die Individualdruckwaage entfallen.In principle, both shut-off valves and the individual pressure compensator can be omitted.
Offenbart sind ein Wegeventil und eine LS-Steueran- ordnung, wobei des Wegeventil mit zwei koaxial zueinander angeordneten VentilSchiebern ausgeführt ist, deren benachbarte Stirnflächen größer als rückwärtige Steuerflächen ausgebildet sind und direkt miteinander in Anlage bringbar sind. Disclosed are a directional control valve and a LS Steueran-, wherein the directional control valve is designed with two coaxial with each other arranged VentilSchiebern whose adjacent end faces are larger than rear control surfaces are formed and can be brought directly into contact with each other.
CTlCTI
Bezugszeichenliste:LIST OF REFERENCE NUMBERS
1 Venti1scheibe1 Venti1scheibe
2 Wegeventil2 way valve
4 VentilSchieber4 valve slide
VentilSchiebervalve slide
8 rechte Zentrierfeder8 right centering spring
10 linke Zentrierfeder10 left centering spring
12 Druckreduzierventil12 pressure reducing valve
14 Druckreduzierventil14 pressure reducing valve
16 Zumeßb1ende16 enlargers
18 Zumeßblende18 metering aperture
20 Individualdruckwaage20 individual pressure scale
22 Druckwaagenfeder22 pressure compensator spring
24 Wechselventil24 shuttle valve
26 LS-Kanal26 LS channel
28 weiteres Wechselventil28 additional shuttle valve
30 Zentraldruckkammer30 central pressure chamber
32 inverses Wechselventil32 inverse shuttle valve
34 Sperrblock34 blocking block
36 Sperrblock36 blocking block
38 Ablaufmessblende38 drainage aperture
40 Ablaufmessblende40 drainage aperture
42 Ventilbohrung42 valve bore
44 Stirnfläche44 face
46 Stirnfläche46 face
48 Federkappe48 spring cap
50 Federkappe50 spring cap
52 Kolbenraum52 piston chamber
54 Kolbenraum54 piston chamber
56 Kölbchen56 cubes
58 Kölbchen58 goblets
60 Steuerfläche60 control surface
62 Steuerfläche62 control surface
64 Mantelbohrung64 casing bore
66 Mantelbohrung Mantelbohrung Mantelbohrung Tankkammer Tankkammer Arbeitskammer Arbeitskammer Zulaufkammer Zulaufkammer Steuerdruckkammer Steuerdruckkammer Steuerkammer Steuerkammer Zentralsteuerkammer Vorlaufkanal Rücklaufkanal Zulaufkanal Druckwaageneingangskammer Federräum Verbindungskanal Vorsteuerkanal Vorsteuerkanal Tanksteuerkante Tanksteuerkante Zulaufsteuerkante Zulaufsteuerkante Steuerkante Steuerkante Ventilkörper Ventilkörper Schließfeder Schließfeder Ventilsitz Ventilsitz Vorsteuerventilkörper Vorsteuerventilkörper Aufstoßkolben 140 Aufstoßkolben66 casing bore Sheath bore Sheath bore Tank chamber Tank chamber Working chamber Working chamber Inlet chamber Inlet chamber Control pressure chamber Control pressure chamber Control chamber Control chamber Central control chamber Flow channel Return channel Supply channel Pressure balance input chamber Spring clearance Connection channel Pilot control channel Pilot control line Tank control edge Inlet control edge Inlet control edge Control edge Control valve Valve body Valve body Closing spring Closing spring Valve seat Valve seat Pilot valve body Pilot valve body Puffing piston 140 toppings
142 Kolbenfläche142 piston area
144 Kolbenfläche144 piston area
145 Steuerkanalabschnitt145 control channel section
148 Steuerkanalabschnitt148 control channel section
150 Federraum 152 Federraum150 spring chamber 152 spring chamber
154 Verbindungsbohrung154 connection hole
156 Verbindungsbohrung156 connecting bore
158 weitere Steuerkante158 more control edge
159 weitere Steuerkante159 more control edge
160 Kammer160 chamber
162 Zusatzsteuerkante 162 additional control edge

Claims

- 22 -Patentansprüche - 22 patent claims
1. Wegeventil mit zwei in einer Ventilbohrung (42) geführten, koaxial zueinander angeordneten Ventilschiebern (4, 6), die in einer Grundposition über eine Zentrierfederanordnung (8, 10) aufeinander zu gespannt sind, und die zum Einstellen einer bestimmten Schieberstellung aus der Grundposition, in der zwei benachbarte Stirnflächen (44, 46) der Ventilschieber1-way valve with two in a valve bore (42) out, coaxially arranged valve spools (4, 6), which are in a basic position via a Zentrierfederanordnung (8, 10) stretched towards each other, and for setting a certain slide position from the basic position in which two adjacent end faces (44, 46) of the valve slide
(4, S) ohne Zwischenschaltung von elastischen Abstützelementen aneinanderliegen oder zueinander benachbart sind, auseinanderbewegbar sind, und die zum Einstellen weiterer Arbeitspositionen gemeinsam verschiebbar sind, dadurch gekennzeichnet, dass die Stirnflächen (44, 46) zum Verschieben in die Schieberstellung mit einem gemeinsamen Steuerdruck beaufschlagbar sind, der auch auf von den Stirnflächen (44, 46) entfernte, mit geringerer Wirkfläche ausgeführte rückwärtige Steuerflächen (60, 62) der Ventil- Schieber (4, 6) wirkt.(4, S) abut each other without the interposition of elastic support elements or adjacent to each other, are moved apart, and which are displaceable for adjusting further working positions together, characterized in that the end faces (44, 46) acted upon for moving into the slide position with a common control pressure are, which also on on the end faces (44, 46) remote, executed with a smaller effective area rear control surfaces (60, 62) of the valve slide (4, 6) acts.
2. Wegeventil nach Patentanspruch 1, wobei zur Bildung der Steuerflächen (60, 62) jeweils ein Endabschnitt der Ventilschieber (4, 6) radial zu einem Zapfen zurückgesetzt ist, der in eine mittelbar oder unmittelbar am Ventilgehäuse (48) abgestützte Kappe eintaucht, so dass durch Kappe und Zapfen ein Raum gebildet ist, der stirnseitig durch die Steuerfläche2. Directional control valve according to claim 1, wherein for forming the control surfaces (60, 62) one end portion of the valve slide (4, 6) is reset radially to a pin which dips into a indirectly or directly on the valve housing (48) supported cap, so that a space is formed by cap and pin, the front side by the control surface
(60, 62) begrenzt ist.(60, 62) is limited.
3. Wegeventil nach Patentanspruch 1, wobei zur Bildung der Steuerflächen (60, 62) in den von den Stirnflächen (44, 46) entfernten Endabschnitten der Ventilschieber (4, 6) Kölbchen (56, 58) geführt sind, - 23 -3. Directional control valve according to claim 1, wherein the formation of the control surfaces (60, 62) in the of the end faces (44, 46) remote end portions of the valve slide (4, 6) Kölbchen (56, 58) are guided, - 23 -
die jeweils mit einem Endabschnitt in einen Kolbenraum (52, 54) der Ventilschieber (4, 6) eintauchen und mit dem anderen Endabschnitt unmittelbar oder mittelbar am Ventilgehäuse (48) abgestützt sind.each with an end portion in a piston chamber (52, 54) of the valve slide (4, 6) dive and with the other end portion directly or indirectly on the valve housing (48) are supported.
4. Wegeventil nach Patentanspruch 1, 2 oder 3, wobei an jedem Endabschnitt der Ventilschieber (1, 2) eine in einem Federraum aufgenommene Zentrierfeder (8) angreift, wobei der Federraum mit Tankdruck beaufschlagt ist.4. Directional control valve according to claim 1, 2 or 3, wherein at each end portion of the valve slide (1, 2) engages a centering spring (8) received in a spring chamber, wherein the spring chamber is acted upon by tank pressure.
5. Wegeventil nach einem der vorhergehenden Patentansprüche, wobei jeder Kolbenraum (52, 54) oder vom Zapfen und Kappe begrenzter Raum über zumindest einen Manteldurchbruch (64, 66; 68, 70) oder Kanal mit dem Steuerdruck und nach einer Verschiebung mit Tankdruck beaufschlagbar ist.5. Directional control valve according to one of the preceding claims, wherein each piston chamber (52, 54) or the pin and cap limited space via at least one sheath opening (64, 66, 68, 70) or channel with the control pressure and after a shift with tank pressure can be acted upon ,
6. Wegeventil nach Patentanspruch 5, wobei der Manteldurchbruch (64, 66; 68, 70) oder Kanal nach der Verschiebung den Kolbenraum (52, 54) bzw. Raum mit dem Federraum der zugeordneten Zentrierfeder (8, 10) verbindet .6. directional control valve according to claim 5, wherein the sheath opening (64, 66, 68, 70) or channel after the displacement of the piston chamber (52, 54) or space with the spring chamber of the associated centering spring (8, 10) connects.
7. Wegeventil nach einem der vorhergehenden Patentansprüche, wobei in der Ventilbohrung (42) zwischen zwei mit einem Tankanschluss (Rl, R2) verbundenen, axial außen liegenden Tankkammern (72, 74) zwei mit jeweils einem Arbeitsanschluss (A, B) verbundene Arbeitskammern (76, 78) , zwei mit einem Druckanschluss7. Directional control valve according to one of the preceding claims, wherein in the valve bore (42) between two with a tank connection (Rl, R2) connected, axially outer tank chambers (72, 74) two each with a working port (A, B) connected working chambers ( 76, 78), two with a pressure port
(P) verbundene Zulaufkammern (80, 82), weitere Steuerkammern (84, 86; 88, 90) sowie eine etwa mittige, mit dem Steuerdruck beaufschlagbare Zentralsteuerkam- mer (92) ausgebildet sind. - 24 -(P) connected inlet chambers (80, 82), further control chambers (84, 86, 88, 90) and an approximately central, can be acted upon with the control pressure Zentralsteuerkam- mer (92) are formed. - 24 -
8. Wegeventil nach Patentanspruch 7, wobei die Zentral- Steuerkammer (92) in der bestimmten Schieberstellung über ein inverses Wechselventil (32) mit den Kolbenräumen (52, 54) der Ventilschieber (4, 6) verbunden ist.8. Directional valve according to claim 7, wherein the central control chamber (92) in the specific slide position via an inverse shuttle valve (32) with the piston chambers (52, 54) of the valve slide (4, 6) is connected.
9. Wegeventil nach einem der vorhergehenden Patentansprüche, mit zwei als Druckreduzierventile (12, 14) ausgebildeten Vorsteuerventilen, über die die Steuerflächen (60, 62) mit einem Steuerdruck beaufschlagbar sind und die in ihrer Grundstellung die Steuerflächen (60, 62) mit Tankdruck verbinden.9. Directional valve according to one of the preceding claims, with two as pressure reducing valves (12, 14) formed pilot valves, via which the control surfaces (60, 62) can be acted upon with a control pressure and connect the control surfaces (60, 62) in their basic position with tank pressure ,
10. LS-Steueranordnung zur Druckmittelversorgung eines an zwei Arbeitsanschlüssen (A, B) angeschlossenen Verbrauchers mit einem Wegeventil (2) nach einem der vorhergehenden Patentansprüche, dem eine Indivi- dualdruckwaage (20) zugeordnet ist.10. LS control arrangement for supplying pressure medium of a consumer connected to two working ports (A, B) with a directional control valve (2) according to one of the preceding claims, which is assigned an individual dual pressure balance (20).
11. LS-Steueranordnung nach Patentanspruch 10, wobei zwischen Wegeventil (2) und zumindest einem der Arbeitsanschlüsse (A, B) ein Sperrblock (34, 36) angeordnet ist . 11. LS control arrangement according to claim 10, wherein between the directional control valve (2) and at least one of the working ports (A, B), a blocking block (34, 36) is arranged.
EP06722721A 2005-04-04 2006-03-30 Directional control valve and control system provided therewith Not-in-force EP1875084B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102005015461 2005-04-04
DE102005029821A DE102005029821A1 (en) 2005-04-04 2005-06-27 Valve has two slides which are spring-loaded towards center of bore and share common control system which allows pressure to be applied simultaneously to their front surfaces and to their rear surfaces, which are smaller in area
PCT/DE2006/000570 WO2006105765A1 (en) 2005-04-04 2006-03-30 Directional control valve and control system provided therewith

Publications (2)

Publication Number Publication Date
EP1875084A1 true EP1875084A1 (en) 2008-01-09
EP1875084B1 EP1875084B1 (en) 2009-02-25

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EP06722721A Not-in-force EP1875084B1 (en) 2005-04-04 2006-03-30 Directional control valve and control system provided therewith

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JP (1) JP2008534887A (en)
AT (1) ATE423913T1 (en)
DE (2) DE102005029821A1 (en)
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WO (1) WO2006105765A1 (en)

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FR2911931B1 (en) * 2007-01-29 2017-04-07 Peugeot Citroen Automobiles Sa PROPORTIONAL STEERING HYDRAULIC DISTRIBUTOR AND METHOD OF MOUNTING SUCH A DISTRIBUTOR
US8245728B2 (en) 2007-05-08 2012-08-21 Raytheon Company Quantum fluid transfer system
DE102007054138A1 (en) 2007-11-14 2009-05-28 Hydac Filtertechnik Gmbh Hydraulic valve device
DE102008031745A1 (en) 2008-07-04 2010-01-07 Hydac Filtertechnik Gmbh Hydraulic valve device
DE102009052257A1 (en) * 2009-11-06 2011-05-12 Claas Industrietechnik Gmbh valve assembly
CN110356985B (en) * 2019-07-16 2020-12-04 徐州阿马凯液压技术有限公司 Load control type rotary valve

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DE2817442A1 (en) * 1978-04-21 1979-10-25 Mainz Gmbh Feinmech Werke Hydraulic or pneumatic control valve - has two spring-loaded coaxial slides movable relatively to each other
DE3365351D1 (en) 1982-12-13 1986-09-18 Vickers Inc Two-stage hydraulic valves
DE3732445C2 (en) 1987-09-25 1993-12-23 Rexroth Mannesmann Gmbh Pressure control valve
JPH03103685A (en) * 1989-09-13 1991-04-30 Tokimec Inc 4-way 4-position electromagnetic pilot switching valve
GB9211898D0 (en) 1992-06-05 1992-07-15 Vickers Systems Ltd Two-stage hydraulic valves
DE19919014C2 (en) * 1999-04-27 2001-03-01 Danfoss Fluid Power As Nordbor Hydraulic valve with a locking and a floating function
ATE298395T1 (en) * 2001-03-21 2005-07-15 Bucher Hydraulics Gmbh WAY VALVE
DE10321914A1 (en) 2003-05-15 2004-12-02 Bosch Rexroth Ag Hydraulic control arrangement
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DK1875084T3 (en) 2009-06-15
DE502006002946D1 (en) 2009-04-09
ATE423913T1 (en) 2009-03-15
EP1875084B1 (en) 2009-02-25
JP2008534887A (en) 2008-08-28
DE102005029821A1 (en) 2006-10-05
WO2006105765A1 (en) 2006-10-12

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