EP1500825A2 - Distributeur à voies multiples - Google Patents

Distributeur à voies multiples Download PDF

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Publication number
EP1500825A2
EP1500825A2 EP04016725A EP04016725A EP1500825A2 EP 1500825 A2 EP1500825 A2 EP 1500825A2 EP 04016725 A EP04016725 A EP 04016725A EP 04016725 A EP04016725 A EP 04016725A EP 1500825 A2 EP1500825 A2 EP 1500825A2
Authority
EP
European Patent Office
Prior art keywords
control
pressure
spring
valve according
directional
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
EP04016725A
Other languages
German (de)
English (en)
Other versions
EP1500825A3 (fr
EP1500825B1 (fr
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 EP1500825A2 publication Critical patent/EP1500825A2/fr
Publication of EP1500825A3 publication Critical patent/EP1500825A3/fr
Application granted granted Critical
Publication of EP1500825B1 publication Critical patent/EP1500825B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • 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

Definitions

  • the invention relates to a directional control valve according to the preamble of claim 1
  • Such directional control valves are for controlling double-acting and single-acting consumers.
  • One Directional control valve with two spools in one spool bore is disclosed in DE 36 29 479 A1. In the basic position the two spools are spaced apart and the two working connections are towards the tank open. In a one-sided operation of the spool is the one spool in the direction of deflected second control slide and takes this after Covering a path corresponding to the distance.
  • the strong middle spring is likely to be the response
  • the known directional control valve adversely affect.
  • Object of the present invention is a directional control valve to provide that eliminates the aforementioned disadvantages and both for controlling double acting as well single-acting consumer is suitable.
  • the basic position are biased, being between the tax pushers arranged a spring device with a spring element is, whose axial length is limited.
  • the spools are by the "bondage" of the centrally arranged spring element only up a certain measure of each other, so that the Control slide in the basic position substantially over the bias of their respective outer spring is subjected to force and a defined basic position taking.
  • the limit is as a drawbar with two movable spring plates executed, via the spring element, preferably a Compression spring, against each shoulder surface of the drawbar are curious.
  • the spool two axially displaceable tensile body which engage with hook-shaped end portions and the maximum length in its limit position of the spring element and thus determine the bias.
  • the gap is advantageously between the be relieved of pressure on both control valves to the tank.
  • the tank holes for pressure relief are preferred trained in the tax pushers.
  • a stop between the two spools, against the the spool when acted upon can be tensioned with a maximum control pressure.
  • a single-acting consumer can be controlled via the directional control valve; and although the one spool is against the stop driven and the second spool is in interaction the spring forces of its outer spring and the middle Spring element as a function of the control pressure emotional.
  • the stopper is a snap ring, the is accommodated in a housing-side inner circumferential groove.
  • a lockable blocking block provided by applying an unblocking control pressure in the outflow direction.
  • the blocking blocks each have a poppet piston, which from the drain side Load pressure can be acted upon, so that the blocking blocks For example, when pulling load a flow control is possible.
  • the directional control valve is a 6-position valve executed.
  • FIG. 1 shows a circuit diagram of an LS system 2, about an unillustrated consumer with pressure medium is available.
  • the LS system 2 has an individual pressure compensator 4, a proportionally adjustable 6-way valve 6 with two spools 8, 10, two pressure control valves 12, 14 and two unlockable Blocking blocks 16, 18 on, beyond the consumer a pump, not shown, pressure medium supplied and over which the pressure medium from the consumer to a not shown tank is traceable.
  • About the pressure control valves 12, 14 may each have a control pressure for moving the spool 8, 10 and an unlock control pressure for switching through the blocking blocks 16, 18 set become.
  • the consumer is a double-acting Differential cylinder, which with its cylinder space on a working connection A and with an annulus to one Work connection B is connected.
  • the pump is on a pressure port P and the tank to a drain port R connected.
  • the control collar 24 has a plurality of control notches, form a control edge 28 and on the one Pressure medium connection from one to the pressure port P connected pressure chamber 30 to an adjacent pressure channel 32, in two to directional control valve 4 leading channels 48, 50 branched, on or is zuu Kunststoffbar.
  • the pressure compensator piston 20 is by means of a at one end of the Pressure balance bore 22 supported control spring 34 in a Biased direction in which the connection between the Pressure chamber 30 and the pressure channel 32 is open.
  • a the Control spring 34 receiving spring chamber 36 is at a first control channel 38 connected to a shuttle valve 40 leads.
  • the two spools 8, 10 are in a slide bore 52 guided axially displaceable.
  • the spools 8, 10 are identical and over a Centering spring assembly 54, 56 in its illustrated Pretensioned basic position, where it has an inventive Spring device 58, to the later reference Figures 3, 4 and 5 will be discussed in detail, spaced apart from each other.
  • the centering spring arrangements 54, 56 each have a centering spring 60, 62, the taken in an end control pressure chamber 64, 66 are.
  • the centering springs 60, 62 immerse each in one cup-like body 68, 70 and support whose inner bottom surface 72, 74 from where they to Housing shoulders 134, 256 with their opposite End section via axially displaceable spring plates 76, 78 attack.
  • the spool 8, 10 can be moved in principle from its basic position mechanically, electrically or hydraulically in a working position.
  • the actuation of the spool 8, 10 hydraulically via in each case an individual control pressure P BX and P AX in the control pressure chambers 64, 66, which are adjusted via the pressure control valves 12, 14.
  • the maximum displacement of the spool 8, 10 is limited by a stop 80 according to the invention in the middle of the spool bore 52.
  • the stopper 80 is formed as a snap ring and housed in an inner circumferential groove of the slide bore 52 fixed to the housing.
  • At least one spool 8, 10th with a not shown odometer for accurate determination provided the respective hub.
  • the slide bore 52 is provided according to the enlarged view in Figure 2 with a plurality of annular spaces.
  • two annular discharge chambers 82, 84 are provided, which are connected via tank channels R to the tank.
  • a respective relief space 86, 88 is arranged, which is also connected to the discharge space 82, 84 with a corresponding position of the spool valve 8, 10.
  • Adjacent to the drainage spaces 82, 84 two further annular spaces are provided, wherein in the following the left is designated as the supply space 90 and the right as the return space 92.
  • two pressure chambers 94, 96 which are connected to the channels 48, 50.
  • the middle annular spaces 116, 122 via connection channels 184, 186 with Entsperrungs concern 180, 182 of the poppet 172, 174 connected, the outer annular spaces 118, 124 are connected to the drain port R and the inner annular spaces 114, 120 are each having a control pressure line 258th , 260 for supplying the control pressure P X.
  • the spools 8, 10 have in the area of the drainage spaces 82, 84 two control collars 98, 100, in their annular end faces each control notches are provided so that at each control collar 98, 100 a flow control edge 102, 104 is formed.
  • the spools 8, 10 In the area of the pressure chambers 94, 96 the spools 8, 10 each have a control collar 106, 108, with a variety of control notches for Forming an inlet control edge 110, 112 is formed.
  • the geometry of the control collars 106, 108 is designed to that in the illustrated basic position of the flow chamber 90th and the return space 92 to the adjacent pressure chamber 94, 96th and to the adjacent discharge space 82, 84 are closed.
  • the blocking blocks 16, 18 are identical and have a locking piston 136, 138, which in a bore 140, 142 out and against a valve seat 144, 146 is biased. In the illustrated blocking position is the connection between a flow chamber 148 and a Working chamber 150 and a working chamber 152 and a Return chamber 154 shut off leak-free.
  • the locking piston 136, 138 are designed as a hollow piston, wherein in a piston crown designed as a cone a pilot cone 156, 158 is guided, which has a pilot spring 160, 162 biased against a pilot seat 164, 166 is. Also, the locking piston 136, 138 on this Pilot springs 160, 162 against their valve seat 144, 146 biased.
  • the pilot poppets 156, 158 each have a projection 168, 170, which in the direction of the lead or return chamber 148, 154 protrudes.
  • the poppet pistons 172, 174 designed as stepped pistons are arranged so as to be axially displaceable, whose piston rods 176, 178 extend in the direction of the projections 168, 170 of the pilot poppets 156, 158.
  • the Aufwinkolben 172, 174 receiving end portions of the bores 140, 142 opens one of the Entsperrungs• 180, 182, which is connected via one of the connecting channels 184, 186 with one of the annular spaces 116, 122 and in the thus the control pressure P X out can be.
  • the flow chamber 148 of the locking block 16 is connected via a Intermediate channel 188 with the flow space 90 and accordingly the return chamber 154 of the locking block 18 via an intermediate channel 190 connected to the return chamber 92.
  • the supply space 90 and the return space 92 are each connected via a control line 192, 194 to the two inputs of the shuttle valve 40. That is, via the shuttle valve 40, the larger of the two in the flow chamber 90 and the return chamber 92 tapped load pressure Y A , Y B is reported in the control channel 38. Furthermore, the load pressures Y A , Y B via control lines 196, 198, which extend between the relief chambers 86, 88 and the control lines 192, 194, to the drain spaces 82, 84 relieved.
  • Figure 3 shows an enlarged and sectioned partial view a preferred embodiment of the invention Spring device 58.
  • the spring device 58 has a limitation for limiting the effective length and thus the bias of a Spring element 200. It has a pull rod 202 with two slidable spring plates 204, 206, which in the illustrated basic position on the spring element 200, preferably a compression spring, in each case against an end side Shoulder surface 208, 210 of the pull rod 202 tensioned are. Thus, the compression spring 200 is over the limit "Tied”.
  • the spring plates 204, 206 surround axially slidably the pull rod 202, so that by displacement at least one of the spring plates 204, 206, the spring 200th can be upset.
  • the bias of the compression spring 200th is chosen so that its biasing force is greater than the Spring force of the centering springs 60, 62 of the spool 8, 10 is at maximum stroke.
  • the spring device 58 is shown in sections in FIG. 4 in a gap 212 between the spools 8, 10 added. To clarify the arrangement the left spool 8 is partially cut shown. The spring device 58 emerges in the basic position the spool 8, 10 sections in each case in a stepped blind hole 216 of the spool 8, 10 and supports with their spring plates 204 an annular surface 218 of the stepped bore 216 from. The axial Distance between the two spools 8, 10 is in the basic position substantially over the axial length the prestressed compression spring 200 determines, wherein due to the bias of the centering springs 60, 62 the Spring plate 204, 206 are supported on the annular surfaces 218.
  • the pull rod 202 is with its end face 220 from the ground 222 of the blind hole 216 spaced so that at an actuation of at least one of the spool 8, 10th move the pull rod 202 toward the bottom 222 can and thus the relative distance between the two Spools 8, 10 can be reduced.
  • the gap 212 is in each case via an axial tank bore 214, the into the bottom 222 of the stepped bore 216 opens and a radial tank bore 224 with the drain chamber 82 in conjunction.
  • the snap ring 80 is in the inner circumferential groove 234 of the slide bore 52 in the middle of the Gap 212 can be seen against which the spool 8, 10 can be brought into abutment position.
  • FIG. 1 Another preferred embodiment of the invention Spring device 58 is shown in FIG.
  • the limitation is carried out by two tensile bodies 226, 228, preferably on the control valves 8, 10th are formed and with hook-shaped end portions 230, 232 mesh.
  • the tensile bodies 226 ', 228 become encompassed by the compression spring 200, the end to End faces 236, 238 of the spool 8, 10 is supported and by the hooking of the two tension bodies 226, 228 biased in limiting function and thus in their axial length is limited.
  • at least one of the spool 8, 10 can accordingly the above-described embodiment of Figures 2 and 3 the compression spring 220 compressed and thus the relative Distance between the spools 8, 10 changed become.
  • FIG. 1 and 2, 6 and 7 show an example "double-acting functions" of the directional control valve 6, for example. when controlling a double-acting lifting cylinder and FIG. 8 shows a "single-acting function", for example. when controlling a single-acting lifting cylinder.
  • Figures 1 and 2 show the directional control valve 4 in prestressed Basic position or in neutral position, in the the blocking blocks 16, 18 are closed and pressure medium between a consumer and the blocking blocks 16, 18 is clamped so that a consumer load safely to the Working connections A, B can be kept.
  • the spool 8, 10 are not supplied with control pressure P BX , P AX and thus centered on the Zentrierfederan füren 54, 56.
  • the connection from the pressure chamber 30 to the pressure channel 32 is closed by the control edge 28.
  • a connection of the flow space 90 and the return space 92 with the discharge spaces 82, 84 via the flow control edges 102, 104 is closed.
  • the load pressures Y A and Y B which are tapped in the flow chambers 90, 92 are guided via the control lines 192, 194, 196, 198 and slide edges of the circumferential grooves 130, 132 to the tank.
  • the unblocking spaces 180, 182 are relieved via the annular grooves 116, 122, slide edges of the circumferential grooves 126, 128 and the annular grooves 118, 124 to the tank.
  • FIG. 6 shows the LS-way valve arrangement 2 in one Work position in which the right working connection B to Tank relieved and the consumer on the left working connection A is supplied with pressure medium.
  • the right spool 10 is acted upon by the control pressure chamber 66 with the control pressure P AX , so that it is moved to the left against the stop 80 and placed in the stop position. Due to the large biasing force of the compression spring 200 this is only negligibly compressed, so that it acts as a transmission element for transmitting the axial deflection of the right spool 10 on the left spool 8. Both spools 8, 10 behave more or less like a common spool and the left spool 8 is deflected to the left in accordance with the movement of the right spool 10. In this case, the channel 50 is closed via the control collar 108 and the intermediate channel 190 of the return chamber 154 is connected via the flow control edge 104 with the discharge space 84.
  • the LS discharge for Y B is closed to the discharge space 84 and the control pressure P X is conducted into the release space 182.
  • the poppet 174 on the pilot poppet 158 lifts it against the force of the pilot spring 162 and against the force acting on the seat load pressure Y B from the pilot seat 166, so that the locking block 18 is controlled in the outflow direction and the outflowing pressure medium from the working chamber 152 can flow into the return chamber 154.
  • the left spool 8 opens its determined by the inlet control edge 110 Zumeßblendenquerrough and pressure fluid flows from the pressure channel 32 in the flow chamber 90 and from there via the blocking block 16 to the consumer.
  • the LS discharge for Y A to the discharge chamber 82 is closed, so that via the control line 192 of the load pressure Y A is guided to the shuttle valve 40 and from there into the spring chamber 36 of the pressure compensator 4.
  • the pressure in the channel 50 is guided into the control chamber 42. Consequently, the pressure compensator 4 takes a corresponding control position in the interaction of the spring force of the control spring 34 and the load pressure Y A with the pressure in the control chamber 42, in which the pressure drop of the feed stream is constant over the Zumeßblende.
  • the supply current to the load is load-independent.
  • the blocking blocks 16, 18 designed so that they work as a pressure regulator can.
  • Block 18 the poppet 174 immersed in tax druckbeaufschlagter Position in sections in the Working chamber 154 and is with the pressure in the Working chamber 154 is applied, so that, depending on the size the opening cross section above the pilot seat 166 and thus changed over the valve seat 146.
  • Figure 7 shows the directional control valve 6 in the clearance, in the the pressure chamber 30 is closed and both working connections A, B, of the consumer with the respective outflow space 82, 84 are connected.
  • the supply and return chambers 148, 152 are connected to the discharge spaces 82, 84 via the discharge control edges 102, 104, the control pressure P X being simultaneously guided into the release chambers 180, 182 and the two blocking blocks 16, 18 through in the flow direction.
  • FIG. 8 shows a working position of the LS system 2 for controlling a single-acting consumer.
  • the right spool 10 is in stop position and the left spool 8 is acted upon by control pressure P BX , that it is transferred against the bias of the central compression spring 200 in a load-holding position, in the working port A opposite the pressure chamber 94 and the drain chamber 82 is.
  • FIG. 1 As already explained in FIGS. 6 and 7, FIG the working connection B in stop position 'of the right Spool 10 is connected to the drain space 84 and thus relieved to the tank, the lock block 18 at the same time acts as a pressure regulator for the flow.
  • the left spool 8 is acted upon independently of the right spool 10 with a control pressure P BX and in a load-holding position, with a corresponding choice of the control pressure P BX the working port A via the inlet control edge 110 with the pressure chamber 94 and thus with the pressure channel 32 (see 6) or via the flow control edge 102 to the drainage space 82 (see FIG.
  • a control pressure P BX control piston 8 is deflected to the right by its center position against the force of the compression spring 200
  • a lifting of a load and a reduction of the control pressure P BX control piston 8 is from its center position by means of the force of the compression spring 200 after shifted left
  • Switching position 240 represents the basic position of the directional control valve 6.
  • the control pressures P AX , P BA are zero and the working ports A, B, the pressure chamber P and the tank port T are closed against each other.
  • the directional control valve 6 When increasing the control pressure P AX , the directional control valve 6 changes over to the switching position 242, in which the pressure chamber P is connected to the working port A and the working port B is connected to the return chamber R. Accordingly, the directional control valve 6 assumes a one-sided increase in the control pressure P BX switch position 244, in which the pressure chamber P is connected to the working port B and the working port A to the return space R.
  • these switching positions 240, 242, 244 allow the control of a double-acting consumer.
  • the directional control valve 6 Upon actuation of the spool 8, 10 with a mean control pressure P BX and a maximum control pressure P AX , the directional control valve 6 assumes the middle position described in FIG. 8 (switch position 246) in which the working port A is shut off and the working port B is depressurized to the tank.
  • the clearance position 248 By increasing the control pressure P BX , the clearance position 248 can be reached, in which also the working port A to the tank depressurized ( Figure 7).
  • the switching position 250 By reducing the control pressure P BX , the switching position 250 can be achieved, in which the pressure chamber P is connected to the working port A.
  • the switching position 250 basically corresponds to the switching position 242, but at a higher control pressure level P AX . Since in the switching positions 246, 248, 250 of the working port B is always connected to the tank, 6 single-acting consumer can be controlled via the directional control valve.
  • the directional control valve 6 With a corresponding mirror-inverted actuation of the directional control valve 6, ie, the control pressure P XB is kept constant at maximum pressure and the control pressure P AX is increased or decreased, the directional control valve 6 assumes switching positions 248, 252, 254 for controlling a simple acting consumer, in which Working port A always connected to the tank and the working port B is connected to the size of the control pressure P AX with the pressure chamber P or the return space R.
  • the directional control valve 6 allows both the Control single-acting as well as double-acting Consumer. Consequently, a variety of Applications.
  • An example is the use the directional control valve 6 for pressure control of implements a tractor or hoists in construction machines, in which, for example, for lifting a cylinder side is pressurized and the other side of the cylinder relieved of pressure.
  • the directional control valve 6 is, for example, suitable for "single - acting functions" in motor applications for free leakage or for position control in single-acting Cylinders.
  • a directional control valve with two in a slide bore Coaxial control slides for control a consumer via two working connections, wherein between the two spools a spring means is provided with a spring element whose Effective length is limited by means of a limitation.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Control Of Fluid Pressure (AREA)
EP04016725A 2003-07-25 2004-07-15 Distributeur à voies multiples Expired - Lifetime EP1500825B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10334056 2003-07-25
DE10334056A DE10334056A1 (de) 2003-07-25 2003-07-25 Wegeventil

Publications (3)

Publication Number Publication Date
EP1500825A2 true EP1500825A2 (fr) 2005-01-26
EP1500825A3 EP1500825A3 (fr) 2005-05-11
EP1500825B1 EP1500825B1 (fr) 2008-05-21

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EP04016725A Expired - Lifetime EP1500825B1 (fr) 2003-07-25 2004-07-15 Distributeur à voies multiples

Country Status (3)

Country Link
EP (1) EP1500825B1 (fr)
AT (1) ATE396341T1 (fr)
DE (2) DE10334056A1 (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006105765A1 (fr) 2005-04-04 2006-10-12 Bosch Rexroth Ag Soupape a tiroirs et dispositif de commande equipe de ladite soupape
EP1710446A3 (fr) * 2005-04-05 2007-03-21 Bosch Rexroth Aktiengesellschaft Commande hydraulique et bloc de commande
DE102007054135A1 (de) 2007-11-14 2009-05-20 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
DE102007054134A1 (de) * 2007-11-14 2009-05-20 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
DE102013014671A1 (de) 2013-09-03 2015-03-05 Hydac Technology Gmbh Ventilbaukomponenten
EP3553325A1 (fr) * 2018-04-13 2019-10-16 The Boeing Company Système hydraulique d'aéronef avec une soupape à double bobine et procédés d'utilisation
EP3561313A1 (fr) * 2018-04-13 2019-10-30 The Boeing Company Système hydraulique d'aéronef avec une soupape à double bobine et procédés d'utilisation
WO2019219492A1 (fr) * 2018-05-18 2019-11-21 Hydac Systems & Services Gmbh Soupape
US10526071B2 (en) 2018-04-13 2020-01-07 The Boeing Company Hydraulic systems and methods to control a member
US10723441B2 (en) 2018-04-13 2020-07-28 The Boeing Company High-speed-deployed, drum-brake, inertia disk for rack and pinion rotational inerter
US10737764B2 (en) 2018-04-13 2020-08-11 The Boeing Company Base flight control member orientation mechanism and control
US10793261B2 (en) 2018-04-13 2020-10-06 The Boeing Company Electro-mechanically biased supercritical flight control surface loading to reduce high pressure actuation cycles
US11072418B2 (en) 2018-04-13 2021-07-27 The Boeing Company Hydraulic system for an aircraft

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Publication number Priority date Publication date Assignee Title
DE102013222149A1 (de) * 2013-10-31 2015-04-30 Robert Bosch Gmbh Hydraulisches Ventil mit Anbauteil am Steuerschieber

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DE3629479A1 (de) 1985-09-03 1987-07-16 Barmag Barmer Maschf Wegeventil
US6408877B2 (en) 1999-12-14 2002-06-25 Bucher Hidroirma S.P.A. Directional control valve

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US3893484A (en) * 1973-07-27 1975-07-08 Sanders Associates Inc Cylinder and piston valve
DE3406794A1 (de) * 1984-02-24 1985-09-05 Mannesmann Rexroth GmbH, 8770 Lohr Druckregelventil
JPS6469878A (en) * 1987-09-10 1989-03-15 Diesel Kiki Co Solenoid proportional pressure control valve
DE9303988U1 (de) * 1993-03-18 1994-07-21 Robert Bosch Gmbh, 70469 Stuttgart Hydraulische Steuereinrichtung mit mindestens einem hydraulisch entsperrbaren Rückschlagventil

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Publication number Priority date Publication date Assignee Title
DE3629479A1 (de) 1985-09-03 1987-07-16 Barmag Barmer Maschf Wegeventil
US6408877B2 (en) 1999-12-14 2002-06-25 Bucher Hidroirma S.P.A. Directional control valve

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006105765A1 (fr) 2005-04-04 2006-10-12 Bosch Rexroth Ag Soupape a tiroirs et dispositif de commande equipe de ladite soupape
EP1710446A3 (fr) * 2005-04-05 2007-03-21 Bosch Rexroth Aktiengesellschaft Commande hydraulique et bloc de commande
DE102007054135A1 (de) 2007-11-14 2009-05-20 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
DE102007054134A1 (de) * 2007-11-14 2009-05-20 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
US8479769B2 (en) 2007-11-14 2013-07-09 Hydac Filtertechnik Gmbh Hydraulic valve device
DE102013014671A1 (de) 2013-09-03 2015-03-05 Hydac Technology Gmbh Ventilbaukomponenten
WO2015032492A2 (fr) 2013-09-03 2015-03-12 Hydac Technology Gmbh Composants de soupape
US10167881B2 (en) 2013-09-03 2019-01-01 Hydac Technology Gmbh Valve components
EP3553325A1 (fr) * 2018-04-13 2019-10-16 The Boeing Company Système hydraulique d'aéronef avec une soupape à double bobine et procédés d'utilisation
CN110374944A (zh) * 2018-04-13 2019-10-25 波音公司 具有双滑阀的飞行器液压***及使用方法
EP3561313A1 (fr) * 2018-04-13 2019-10-30 The Boeing Company Système hydraulique d'aéronef avec une soupape à double bobine et procédés d'utilisation
US10526071B2 (en) 2018-04-13 2020-01-07 The Boeing Company Hydraulic systems and methods to control a member
US10711809B2 (en) * 2018-04-13 2020-07-14 The Boeing Company Aircraft hydraulic system with a dual spool valve and methods of use
US10723441B2 (en) 2018-04-13 2020-07-28 The Boeing Company High-speed-deployed, drum-brake, inertia disk for rack and pinion rotational inerter
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ATE396341T1 (de) 2008-06-15
EP1500825A3 (fr) 2005-05-11
EP1500825B1 (fr) 2008-05-21
DE502004007201D1 (de) 2008-07-03
DE10334056A1 (de) 2005-02-10

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