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EP0088017A2 - Hydraulisches Wegeschieberventil - Google Patents

Hydraulisches Wegeschieberventil Download PDF

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Publication number
EP0088017A2
EP0088017A2 EP83400385A EP83400385A EP0088017A2 EP 0088017 A2 EP0088017 A2 EP 0088017A2 EP 83400385 A EP83400385 A EP 83400385A EP 83400385 A EP83400385 A EP 83400385A EP 0088017 A2 EP0088017 A2 EP 0088017A2
Authority
EP
European Patent Office
Prior art keywords
drawer
chamber
source
screw
bore
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
EP83400385A
Other languages
English (en)
French (fr)
Other versions
EP0088017A3 (en
EP0088017B1 (de
Inventor
Claude Bouveret
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.)
Compagnie Parisienne dOutillage a Air Comprime SA
Original Assignee
Compagnie Parisienne dOutillage a Air Comprime SA
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 Compagnie Parisienne dOutillage a Air Comprime SA filed Critical Compagnie Parisienne dOutillage a Air Comprime SA
Publication of EP0088017A2 publication Critical patent/EP0088017A2/de
Publication of EP0088017A3 publication Critical patent/EP0088017A3/fr
Application granted granted Critical
Publication of EP0088017B1 publication Critical patent/EP0088017B1/de
Expired 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
    • F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
    • F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
    • F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
    • F15B9/10—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor in which the controlling element and the servomotor each controls a separate member, these members influencing different fluid passages or the same passage

Definitions

  • the present invention relates to a device for controlling the displacement of a rod of a hydraulic amplifier intended for piloting an apparatus.
  • the invention is intended to apply to displacements of small amplitude (from a few centimeters to a few decimeters).
  • An object of the invention is to provide a control device having a volume as small as possible, both in its transverse dimensions and in its longitudinal dimensions.
  • Another object of the invention is to provide a control device making it possible to ensure high precision of movement of the rod, for example of the order of a hundredth of a millimeter.
  • a device for moving a cylinder rod with hydraulic amplification comprising a double action cylinder having an inlet and an outlet for a pressurized fluid, a hollow differential piston dividing the cylinder into a first chamber connected to the inlet and a second chamber, the piston having a first small surface and a second large surface delimiting the two chambers and a rod emerging from the cylinder, the piston comprising inside a helical screw having a groove in communication with the second chamber, the piston having a first orifice connecting the groove to the first chamber, when the screw turns in a given direction and a second orifice connecting the groove to the second chamber when the screw turns in the other direction, the rotations of the screw cause movements piston in either direction.
  • Such a device lends itself poorly to miniaturization, due in particular to the fact that almost all of the high pressure and return hydraulic circuits are arranged around the piston rod or inside this rod.
  • all of the hydraulic circuits are arranged inside the piston.
  • the invention relates to a device for controlling the displacement of a rod of a hydraulic amplifier comprising a movable piston in a cylinder, said piston dividing the cylinder into a first and a second chamber, said piston having a first face constituting a movable wall of the first chamber and a second face of cross section greater than that of the first face and constituting a movable wall of the second chamber, the piston rod passing through the cylinder via a sealed passage, said piston being provided with a cylindrical axial cavity, said cylinder being provided with a first pipe connecting the interior of the cylinder to a source of pressurized fluid and a second pipe connecting the interior of the cylinder to a return tank, characterized in that the piston is provided with means for bringing the first or the second chamber into communication, depending on the direction of rotation of a motor with the pressure source, driving the piston in either direction respectively, said means being completely inside said piston.
  • said means is a helical groove screw driven by said motor, said screw rotating in said cavity, said piston comprising a first inner pipe making the first face communicate with the cavity and a second pipe making communicate the inside the cavity with an annular recess in the piston made in line with the second pipe, the orifices of said pipes in the cavity being spaced at least one step from the groove of the screw.
  • the orifices of said pipes are spaced apart by a length equal to p (N + 0.5) - 2d, where p is the pitch of the screw, d the diameter of the orifices and N is an integer.
  • said means comprises a drawer linked to the motor shaft by a link allowing it to move in rotation but leaving it free in translation, the drawer being secured to a threaded part screwing into a threaded bore of the cylinder, said drawer being provided with a pipe connecting the interior of the cavity to said first chamber, the piston being provided with a pipe connecting the second chamber to the cavity and opening into the cavity in line with an annular recess in the drawer.
  • the invention applies to a hydraulic distribution device for the operation of a hydraulic receiver such as a jack, in which the preceding piston is further provided with recesses arranged in the vicinity of pipes formed in the cylinder body and connected to a source of pressurized fluid, to a return, to the inlet and the outlet of a hydraulic receiving device .
  • the control device shown in Figure 1 comprises a cylinder 1 having an axial bore 2 in which can slide a piston 3 having a small face 3A and a large face 3B.
  • the piston is connected to a rod 4 which leaves the cylinder via a sealed passage (the conventional sealing means are not shown); the rod is terminated by a mandrel 4A which can be connected to the device controlled by the device according to the invention.
  • the piston delimits on the side of face A a first chamber 5 and on the side of face 3B a second chamber 6.
  • a screw 9 called “drawer screw”, this screw comprising a helical thread or ramp whose raised part is referenced 9A, while the hollow part is designated at 9B and opens into the second bedroom 6.
  • the screw 9 can be driven in a rotational movement inside the bore 7 by any suitable member 10 such as an electric motor for example of the stepping type, with digital control, or an associated direct current motor. to an encoder.
  • a shaft 11 provides the mechanical connection between the member 10 and the screw 9, the seal being provided at by means of a low friction seal 12.
  • a bearing 12A supports the longitudinal forces due to the pressure.
  • first chamber 5 communicates on the one hand with a source of pressurized fluid P (not shown) by means of a first pipe 13 machined in the body 1 and on the other hand with a first pipe 14, the outlet orifice is disposed at the level of screw 8.
  • the periphery of the part 3A of the piston 3 comprises an annular recess 15 communicating on the one hand with a cover for the return of the fluid under atmospheric pressure T, and this by means of a second pipe 16 machined in the body 1, and on the other hand with a second pipe 18 whose outlet orifice is also disposed at the level of the screw 9.
  • the diameter of the orifices of the pipes 14 and 17 is substantially equal to half the width of the thread of the screw 9, ie a quarter of the pitch.
  • the distance between the orifices of the pipes 14 and 17 is given by the relation: P (N + 0.5) - 2d in which p is the pitch of the thread of the screw 9, N is an integer (generally equal to 1) and d is the diameter of said orifices in the pipes 14.
  • the device according to the invention makes it possible to transform any rotary movement into a linear movement by hydraulic tracking of the helical thread of the slide screw 9. It therefore has a large number of advantages.
  • FIG 2 shows an alternative embodiment.
  • the elements common to Figures 1 and 2 have been given the same reference numbers.
  • the screw 9 in FIG. 1 is replaced by a distribution slide 29 provided with a recess 29A of longitudinal dimension close to the spacing of the pipes 14 and 17 and an internal conduit 29B for balancing the pressures on the part and d other from the drawer.
  • the drawer is linked in rotation to the motor shaft 10 by a key coupling member 30 which leaves the drawer free in translation.
  • the drawer has a threaded part 31 which is screwed into a threaded part.
  • a bearing 30A absorbs the longitudinal forces.
  • a 30B seal provides sealing.
  • a channel 30C ensures pressure balancing on either side of the threaded part 31.
  • the piston comprises a conduit 17A opening on one side to the right of the recess and on the other in the chamber 6.
  • a rotation of the motor 10 in direction f causes a displacement of the slide in translation to the right and a displacement of the piston to the right (arrow F).
  • a rotation of the motor in opposite direction (f t ) produces a displacement of the piston towards the left (F ').
  • the motor is preferably a stepping motor or a direct current motor associated with an encoder.
  • the invention which has just been described applies in particular to the production of a hydraulic distribution device and more particularly a hydraulic distribution device with a spool of the servo-valve type capable of providing a fluid flow rate, proportional to a quantity of pulses transmitted by a control member, for example a motor of the control stepping type. It suffices to replace the piston of FIGS. 1 and 2 with a hydraulic distribution slide.
  • FIG. 1 A first embodiment of such a distributor is shown in FIG. 1.
  • the reference 100 designates a body of circular section closed at one of its ends by a cap 102.
  • a bore 103 receiving a fur 104, seals such as 105 being advantageously disposed between said body 100 and said fur 104.
  • a first bore 109 is capable of receiving a screw 110 with a helical thread, the raised and recessed portions of said thread being referenced 111A and 111B respectively, said screw 110 being linked by means of a shaft 112 to a rotary drive means 113 such as a digitally controlled stepping motor, an O-ring 114 ensuring the tightness of said shaft 112.
  • a rotary drive means 113 such as a digitally controlled stepping motor
  • O-ring 114 ensuring the tightness of said shaft 112.
  • the bottom of said bore 109 constitutes a first chamber 115.
  • a second bore 116 is made in the drawer 108 opposite the first bore 109, a member known as a feedback needle 117 being disposed in this bore 116 and coming to bear via one of its ends against the bottom of the cap 102, the space delimited by the other end of the feedback needle 117 and the bottom of the second bore 116 constituting a second chamber 118 whose section is substantially half of the section of the first room 115.
  • Figure 3 also shows that in the body 100 and the fur 104 are successively formed a central groove 120 communicating with a source of pressurized oil P via a line 121, two grooves called use being arranged on either side of the central groove 120, a first groove 122 and a second groove 123 communicating by way of example, each with one of the compartments of a jack (not shown) and this by means of lines 124 and 125 respectively, and finally two extreme grooves 126 and 127 communicating with an oil tank under atmospheric pressure T, and this via lines 128 and 129 respectively.
  • the periphery of the drawer 108 comprises a first median annular recess 130, as well as a second 131 and a third 132 annular recesses arranged on either side of the median recess 130.
  • the central recess 130 communicates on the one hand with a first pipe 133 whose outlet orifice opens at the level of the screw 110 and on the other hand with a second pipe 134 opening into said chamber 118 of the second bore 116.
  • the second recess 131 communicates with a pipe 135, the outlet orifice of which also opens at the level of the screw 110.
  • the diameter of the orifices of the pipes 133 and 135 is substantially equal to half the width of the thread of the screw 110, ie a quarter of the pitch of said screw.
  • the distance between the orifices of pipes 133 and 135 is given by the relation: p (N + 0.5) - 2d in which p is the pitch of the thread of the screw 110, N is an integer (generally equal to 1) and d is the diameter of the said orifices in the pipes 133 and 135.
  • a pipe 143 machined in the body 100 makes it possible to put the front and rear parts of the drawer 108 in communication and thus to drain outwards the oil leaks spreading inside the cap 102 in particular.
  • the pressure P prevailing in the second chamber 118 will therefore move the drawer 108 to the left, thus communicating the median annular recess 130 with the groove 123 communicating via the conduit 125 for example with one of the compartments of the jack (not shown), while the annular recess 132 communicating with the groove 127 and the pipe 129 will connect the groove 122 and the pipe 124 connected to the other compartment of the jack at atmospheric pressure.
  • the device according to the invention makes it possible to transform any rotary movement into a linear movement by following the helical thread of the screw 110. It therefore has the advantages previously listed.
  • FIG. 4 represents an alternative embodiment in which the screw is replaced by a micro-drawer 229; the elements common to Figures 3 and 4 have been given the same reference numbers.
  • the micro-slide 229 is connected to the shaft of the motor 113 by a key 230 which provides a rotation drive but retains freedom of translation.
  • a 230A bearing absorbs longitudinal forces; a 230B seal provides sealing.
  • the drawer is provided with a threaded part 231 which is screwed into a threaded bore of the body 1.
  • a conduit 230C ensures pressure balance on either side of the threaded part 231.
  • the micro-drawer is provided with a recess 229A; the drawer 108 has a pipe 232 opening on one side to the right of the recess 229A and on the other in the chamber 115.
  • a rotation of the motor in the direction of the arrow f causes the micro-slide to move to the left, which has the effect of connecting the chamber 115 to atmospheric pressure via the line 232, the recess 229A, the line 135, groove 126 and channel 128.
  • the drawer will be moved to the left.
  • a rotation of the motor in the direction of arrow f will result in a translation of the drawer to the right.
  • the amplitude of the translation is strictly proportional to the angle of rotation of the motor. We find the same advantages as before.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transmission Devices (AREA)
EP19830400385 1982-02-26 1983-02-25 Hydraulisches Wegeschieberventil Expired EP0088017B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
FR8203239 1982-02-26
FR8203239 1982-02-26
FR8205928 1982-04-06
FR8205928 1982-04-06

Publications (3)

Publication Number Publication Date
EP0088017A2 true EP0088017A2 (de) 1983-09-07
EP0088017A3 EP0088017A3 (en) 1984-04-04
EP0088017B1 EP0088017B1 (de) 1987-11-19

Family

ID=26222776

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19830400385 Expired EP0088017B1 (de) 1982-02-26 1983-02-25 Hydraulisches Wegeschieberventil

Country Status (2)

Country Link
EP (1) EP0088017B1 (de)
DE (1) DE3374578D1 (de)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0117208A1 (de) * 1983-02-17 1984-08-29 COMPAGNIE PARISIENNE D'OUTILLAGE A AIR COMPRIME Société anonyme dite: Hydraulischer Servodruckbegrenzer
EP0117207A1 (de) * 1983-02-17 1984-08-29 COMPAGNIE PARISIENNE D'OUTILLAGE A AIR COMPRIME Société anonyme dite: Hydraulische Verteilereinrichtung
EP0117209A1 (de) * 1983-02-17 1984-08-29 COMPAGNIE PARISIENNE D'OUTILLAGE A AIR COMPRIME Société anonyme dite: Servostromregler
FR2544444A1 (fr) * 1983-04-13 1984-10-19 Integral Hydraulik Co Distributeur electrohydraulique proportionnel a deux etages
FR2547664A1 (fr) * 1983-06-17 1984-12-21 Outillage Air Comprime Servoregulateur de debit
DE3339578A1 (de) * 1983-11-02 1985-05-09 Volkswagenwerk Ag, 3180 Wolfsburg Einrichtung zur verdichtungssteuerung
EP0296104A1 (de) * 1987-06-16 1988-12-21 SIG Schweizerische Industrie-Gesellschaft Hydraulischer Linear-Servoverstärker
WO1991014103A1 (de) * 1990-03-10 1991-09-19 Schnuerle Friedhelm Pneumatische oder hydraulische kolben-zylinder-einheit mit servosteuerung
WO1993019300A1 (en) * 1992-03-23 1993-09-30 C.W.F. Hamilton & Co. Limited Hydraulic cylinder feedback control
EP0767310A3 (de) * 1995-10-07 1999-09-01 EUROCOPTER DEUTSCHLAND GmbH Hydraulischer Stellantrieb
EP0894982A3 (de) * 1997-07-29 2000-05-24 Ebara Corporation Hydraulische Servoeinrichtung
FR2806760A1 (fr) * 2000-03-24 2001-09-28 Imeca Dispositif de commande en deplacement d'une tige de verin actionneur
WO2008088447A1 (en) * 2006-12-22 2008-07-24 Caterpillar Inc. Rotary-actuated electro-hydraulic valve
US8074558B2 (en) 2008-04-30 2011-12-13 Caterpillar Inc. Axial piston device having rotary displacement control
EP2848821A1 (de) * 2013-09-12 2015-03-18 Start Elevator S.r.l. Regelventil für Hydraulikkreise zur Versorgung von Hebeanlagen

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3106224A (en) * 1960-08-02 1963-10-08 Plessey Co Ltd Servo operated hydraulic valves
GB1116632A (en) * 1965-10-12 1968-06-12 Chandler Evans Inc Fluid-pressure servo-motor positioning apparatus
US3511132A (en) * 1967-11-18 1970-05-12 Rexroth Gmbh G L Hydraulic power amplifier
BE758863A (fr) * 1970-08-27 1971-04-16 Saito Tadashi Structure et procede de fabrication de cylindre a pulsations a pressionpar fluide destine au controle de valeur,
DE2051582A1 (de) * 1970-10-21 1972-07-06 Schneider Co Optische Werke Folgekolbenventil
FR2268966A1 (en) * 1974-11-29 1975-11-21 Poclain Sa Hydraulically operated ram - has main rod with bore accommodating rotary auxiliary rod with spiral grooves and ramps
US4245547A (en) * 1977-10-31 1981-01-20 Commercial Shearing, Inc. Rotary to linear servo mechanisms

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0117208A1 (de) * 1983-02-17 1984-08-29 COMPAGNIE PARISIENNE D'OUTILLAGE A AIR COMPRIME Société anonyme dite: Hydraulischer Servodruckbegrenzer
EP0117207A1 (de) * 1983-02-17 1984-08-29 COMPAGNIE PARISIENNE D'OUTILLAGE A AIR COMPRIME Société anonyme dite: Hydraulische Verteilereinrichtung
EP0117209A1 (de) * 1983-02-17 1984-08-29 COMPAGNIE PARISIENNE D'OUTILLAGE A AIR COMPRIME Société anonyme dite: Servostromregler
FR2544444A1 (fr) * 1983-04-13 1984-10-19 Integral Hydraulik Co Distributeur electrohydraulique proportionnel a deux etages
FR2547664A1 (fr) * 1983-06-17 1984-12-21 Outillage Air Comprime Servoregulateur de debit
DE3339578A1 (de) * 1983-11-02 1985-05-09 Volkswagenwerk Ag, 3180 Wolfsburg Einrichtung zur verdichtungssteuerung
EP0296104A1 (de) * 1987-06-16 1988-12-21 SIG Schweizerische Industrie-Gesellschaft Hydraulischer Linear-Servoverstärker
US4907492A (en) * 1987-06-16 1990-03-13 Sig Schweizerische Industrie-Gesellschaft Apertured valve disposed in hollow piston rod of follower-type motor
WO1991014103A1 (de) * 1990-03-10 1991-09-19 Schnuerle Friedhelm Pneumatische oder hydraulische kolben-zylinder-einheit mit servosteuerung
WO1993019300A1 (en) * 1992-03-23 1993-09-30 C.W.F. Hamilton & Co. Limited Hydraulic cylinder feedback control
EP0767310A3 (de) * 1995-10-07 1999-09-01 EUROCOPTER DEUTSCHLAND GmbH Hydraulischer Stellantrieb
EP0894982A3 (de) * 1997-07-29 2000-05-24 Ebara Corporation Hydraulische Servoeinrichtung
FR2806760A1 (fr) * 2000-03-24 2001-09-28 Imeca Dispositif de commande en deplacement d'une tige de verin actionneur
WO2008088447A1 (en) * 2006-12-22 2008-07-24 Caterpillar Inc. Rotary-actuated electro-hydraulic valve
US7735517B2 (en) 2006-12-22 2010-06-15 Caterpillar Inc Rotary-actuated electro-hydraulic valve
US8074558B2 (en) 2008-04-30 2011-12-13 Caterpillar Inc. Axial piston device having rotary displacement control
EP2848821A1 (de) * 2013-09-12 2015-03-18 Start Elevator S.r.l. Regelventil für Hydraulikkreise zur Versorgung von Hebeanlagen

Also Published As

Publication number Publication date
EP0088017A3 (en) 1984-04-04
EP0088017B1 (de) 1987-11-19
DE3374578D1 (en) 1987-12-23

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