WO2006105765A1 - Soupape a tiroirs et dispositif de commande equipe de ladite soupape - Google Patents

Soupape a tiroirs et dispositif de commande equipe de ladite soupape Download PDF

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Publication number
WO2006105765A1
WO2006105765A1 PCT/DE2006/000570 DE2006000570W WO2006105765A1 WO 2006105765 A1 WO2006105765 A1 WO 2006105765A1 DE 2006000570 W DE2006000570 W DE 2006000570W WO 2006105765 A1 WO2006105765 A1 WO 2006105765A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
control
pressure
chamber
slide
Prior art date
Application number
PCT/DE2006/000570
Other languages
German (de)
English (en)
Inventor
Heinrich Lödige
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
Priority to DK06722721T priority Critical patent/DK1875084T3/da
Priority to EP06722721A priority patent/EP1875084B1/fr
Priority to DE502006002946T priority patent/DE502006002946D1/de
Priority to JP2008504612A priority patent/JP2008534887A/ja
Publication of WO2006105765A1 publication Critical patent/WO2006105765A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/021—Valves for interconnecting the fluid chambers of an actuator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid 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
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0433—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being pressure control valves

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)
  • Float Valves (AREA)
  • Massaging Devices (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

Soupape à tiroirs et dispositif de commande LS. Ladite soupape est pourvue de deux tiroirs disposés coaxialement, dont les faces avant voisines sont plus grandes que les faces de commande arrière et peuvent être amenées en contact directement l'une avec l'autre.
PCT/DE2006/000570 2005-04-04 2006-03-30 Soupape a tiroirs et dispositif de commande equipe de ladite soupape WO2006105765A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DK06722721T DK1875084T3 (da) 2005-04-04 2006-03-30 Retningsventil og LS-styreindretning udfört dermed
EP06722721A EP1875084B1 (fr) 2005-04-04 2006-03-30 Soupape a tiroirs et dispositif de commande equipe de ladite soupape
DE502006002946T DE502006002946D1 (de) 2005-04-04 2006-03-30 Wegeventil und damit ausgeführte ls-steueranordnung
JP2008504612A JP2008534887A (ja) 2005-04-04 2006-03-30 方向制御弁および方向制御弁を備えた制御装置

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102005015461 2005-04-04
DE102005015461.1 2005-04-04
DE102005029821A DE102005029821A1 (de) 2005-04-04 2005-06-27 Wegeventil und damit ausgeführte LS-Steueranordnung
DE102005029821.4 2005-06-27

Publications (1)

Publication Number Publication Date
WO2006105765A1 true WO2006105765A1 (fr) 2006-10-12

Family

ID=36645583

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2006/000570 WO2006105765A1 (fr) 2005-04-04 2006-03-30 Soupape a tiroirs et dispositif de commande equipe de ladite soupape

Country Status (6)

Country Link
EP (1) EP1875084B1 (fr)
JP (1) JP2008534887A (fr)
AT (1) ATE423913T1 (fr)
DE (2) DE102005029821A1 (fr)
DK (1) DK1875084T3 (fr)
WO (1) WO2006105765A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009062563A1 (fr) * 2007-11-14 2009-05-22 Hydac Filtertechnik Gmbh Vanne hydraulique
DE102008031745A1 (de) 2008-07-04 2010-01-07 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2911931B1 (fr) * 2007-01-29 2017-04-07 Peugeot Citroen Automobiles Sa Distributeur hydraulique a pilotage proportionnel et procede de montage d'un tel distributeur
US8245728B2 (en) 2007-05-08 2012-08-21 Raytheon Company Quantum fluid transfer system
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ATE423913T1 (de) 2009-03-15
EP1875084B1 (fr) 2009-02-25
DE502006002946D1 (de) 2009-04-09
DK1875084T3 (da) 2009-06-15
EP1875084A1 (fr) 2008-01-09
JP2008534887A (ja) 2008-08-28
DE102005029821A1 (de) 2006-10-05

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