EP0471695B1 - Entrainement hydraulique - Google Patents

Entrainement hydraulique Download PDF

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Publication number
EP0471695B1
EP0471695B1 EP90906855A EP90906855A EP0471695B1 EP 0471695 B1 EP0471695 B1 EP 0471695B1 EP 90906855 A EP90906855 A EP 90906855A EP 90906855 A EP90906855 A EP 90906855A EP 0471695 B1 EP0471695 B1 EP 0471695B1
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EP
European Patent Office
Prior art keywords
measuring system
reference value
value setting
drive
shaft
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Expired - Lifetime
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EP90906855A
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German (de)
English (en)
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EP0471695A1 (fr
Inventor
Hans Hartmann
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Individual
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Individual
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Priority to AT90906855T priority Critical patent/ATE93584T1/de
Publication of EP0471695A1 publication Critical patent/EP0471695A1/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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/28—Means for indicating the position, e.g. end of stroke
    • 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
    • F15B9/09—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 with electrical control means
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T408/00—Cutting by use of rotating axially moving tool
    • Y10T408/65—Means to drive tool
    • Y10T408/675—Means to drive tool including means to move Tool along tool-axis
    • Y10T408/6757—Fluid means
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T409/00—Gear cutting, milling, or planing
    • Y10T409/40—Broaching
    • Y10T409/406475—Cutter infeed means
    • Y10T409/40665—Imparting rectilinear motion to cutter
    • Y10T409/407—Fluid powered means
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T82/00—Turning
    • Y10T82/25—Lathe
    • Y10T82/2531—Carriage feed
    • Y10T82/2533—Control

Definitions

  • Such a hydraulic drive device is known from DE-A-3438 600.
  • the piston of a hydraulic motor which is firmly coupled to the tool, is controlled by means of a follow-up control valve which works with an electromechanically controllable position setpoint specification for the movable drive element of the hydraulic motor and with mechanical actual position feedback.
  • a threaded spindle and a spindle nut which meshes with its thread are provided for the position setpoint specification and actual value feedback, one of these two elements - the spindle nut system - being drivable by means of an electric motor in the sense of the position setpoint specification and the other of these two elements can be driven in the sense of the actual position feedback, such that that when the rate of change of the position setpoint specification and the position actual value feedback are balanced, the spindle and the nut rotate at the same speed and do not perform any relative axial movements with respect to one another.
  • a valve actuator is provided which, when the spindle and the nut rotate at different speeds, also carries out relative movements of the nut against the spindle and thereby the valve in the sense of an increase in the flow cross sections of supply paths via which the pressure medium Achievement of the desired direction of movement flows, controlled when the rate of change of the actual position is smaller than the change in the position setpoint specification, and keeps these flow cross-sections constant if and as long as these rates of change are the same.
  • the signals required for the motion control of the electric motor are generated by an electronic control unit which is provided with an interface which enables a signal transition and / or data exchange between an NC or a CNC control and the electronic control unit.
  • a monitoring device is provided in which the distance of the control valve actuating element from its basic position is monitored and if this distance defines a predefinable, defined one Falls below the minimum value, which is equivalent to the fact that the tool approaches the dead center, triggers a position-characteristic monitoring signal from a proximity switch.
  • the object of the invention is therefore to improve a drive device of the type mentioned in such a way that a continuous and continuous detection of the following error ⁇ S is possible.
  • the monitoring device comprises a rotary position transmitter which, e.g. generates output signals in digital format which are a direct measure of the total number of revolutions carried out by the setpoint specification element and their azimuthal position within each revolution, and an electronic displacement sensor is also provided, the output signals of which are a direct measure of the axial deflection of the setpoint value Default element relative to the neutral position of the same or the neutral position of the valve actuating element and thus a measure for the following error ⁇ S are by which the actual position of the tool or the drive element of the hydraulic motor lags behind its target position.
  • the drive device offers the possibility of recognizing an impending malfunction of the machine equipped with it as a whole and of course also the - timely - avoidance of this malfunction, which could be linked to damage to the machine.
  • This control unit enables the drive device z. B. in the sense of the best possible compromise between desired high dynamics and nonetheless gentle operation.
  • the preferred design of the rotary position sensor provided for monitoring the position setpoint value and the arrangement of its rotating sensor elements on the setpoint value shaft of the overrun control valve of the drive device has the advantage of very precise detection of the relevant position setpoint value - ultimately -
  • the tool since no gears or transmission elements, which may be subject to slip or play, are connected between the position setpoint input shaft and the rotary position transmitter.
  • the working medium of the drive device can be used in a simple manner for cooling the control motor, which is thereby controlled with higher electrical power can, which in turn benefits the dynamics of the entire drive device.
  • the features of claim 8 indicate a preferred, special design of the rotary position transmitter provided for monitoring the position setpoint specification, which enables an angular resolution of the rotary position of 3.6 ⁇ 10 ⁇ 20.
  • the basic structure is gradually specified by those of claim 10 in terms of a preferred embodiment of the displacement sensor, by means of which the following error ⁇ S of the drive device can be detected, the following error ⁇ S being accurate to at least 1/100 of its maximum amount is measurable.
  • the evaluation of the displacement sensor output signal provided in accordance with claim 11 means that the neutral position of the valve actuating element of the follower control valve can not be assigned to a specific output signal level of the displacement sensor, so that time-consuming adjustment and calibration processes can be dispensed with.
  • the hydraulic drive device according to the invention shown in FIG. 1, to the details of which is expressly referred to, is designated overall by 10 and consists of a hydraulic motor 11, a follow-up control valve 12 which, with an electrically controlled specification of the desired value of the position of a tool (not shown) , which is brought into its working positions by means of the hydraulic motor 11, and mechanical position actual value feedback operates, an electronic control unit 13 for the position setpoint specification control, which is only indicated schematically, and a measuring system, designated overall by 14, by means of which, on the one hand, the controlled one
  • the desired position value of the tool or the drive piston 16 can be measured and, on the other hand, the following error ⁇ S can be detected, by which the tool or the drive piston 16 lags the controlled position desired value.
  • the follow-up control valve 12 and the measuring system are designed as a compact structural unit accommodated in a common housing 17, the follow-up control valve 12 along the seen central axis 18 of the assembly 11, 12, 14, "between” the hydraulic motor 11 and the measuring system 14 is arranged.
  • the follow-up control valve 12 is a 4/3-way valve in its function, the neutral basic position 0 is its blocking position, in which both drive pressure chambers 21 and 22 of the hydraulic motor 11 both against the P connection 23 and against the T connection 26 of the pressure supply unit are blocked.
  • the drive pressure chamber 21 on the left according to FIG. 1 is via a flow path 32 of the follow-up control valve 12 connected to the - unpressurized - tank connection 26 of the pressure supply unit 24, while the other drive pressure chamber 22 of the hydraulic cylinder 11 is connected to the P-pressure outlet 23 of the pressure supply unit 24 via the second flow path 33 which is effective in the functional position II of the overrun control valve 12.
  • the drive piston 16 of the hydraulic motor 11 moves in the direction of the arrow 28, according to FIG. 1, to the left.
  • a hollow shaft 37 is mounted rotatably and axially displaceably in a central bore 36, coaxial with the longitudinal axis 18 of the drive device 10, of a block-shaped central section 17 ′′ of the housing 17 which forms on the housing of the follow-up control valve 12 and which on its side faces the hydraulic motor 11 End portion is provided with an internal thread 38, via which it is in meshing engagement with a central, elongated threaded spindle 39 which is fixedly connected to the drive piston 16 of the hydraulic motor 11.
  • This hollow shaft 37 can be driven - for specifying the position setpoint of the drive piston 16 of the hydraulic motor 11 - by means of an electric motor designated overall by 41, the power supply of which is controlled by electrical output signals of the electronic control unit 13 in the sense of the position setpoint specification.
  • this electric motor has a stator 42 arranged fixed to the housing and an axially reciprocable rotor 43, the rotor shaft of which is formed by a section of the hollow shaft 37, which is connected to the rotor 43 so as to be fixed in terms of rotation and displacement.
  • the rotor 43 of the electric motor 41 is thus in a central position via the section 44 of the hollow shaft 37 axially penetrated by the threaded spindle 39 on the block-shaped central section 17 ′′ of the housing 17, on the one hand, and on the other hand with a further section 46 of the hollow shaft 37 carrying the rotor 43 Bore 47 of an intermediate wall 48 of the housing 17 is rotatably mounted, which essentially delimits the space 49 occupied by the motor 41 and the overrun control valve 12 from the housing space 51 provided for accommodating the measuring system 14, these spaces 49 and 41 not being pressure-tight are closed against each other, but overall form the leak oil chamber of the drive device 10.
  • axially displaceable but non-rotatable is a generally designated 52 yoke-shaped valve actuating member, which has two parallel yoke legs 53 and 54 has that through a parallel to!
  • Central longitudinal axis 18 of the drive device extending guide rod 56 which passes through a radially lateral guide bore 57 of the block-shaped, central housing part 17 '', are firmly connected to one another and engage axially on each of the opposite sides of the valve piston 34 via an actuating pin 58 or 59 , wherein this support of the yoke legs 53 and 54 on the actuating pins 58 and 59 and the valve piston 34 is a positive fit.
  • the two yoke legs 53 and 54 have aligned, with the central longitudinal axis 18 of the drive device 10 coaxial bores 61 and 62, the diameter of which is slightly larger than the outer diameter of the hollow shaft 37, so that this with a sufficient for their smooth rotation through these holes 61 and 62 of the yoke legs 53 and 54 of the valve actuating member 52 can pass through.
  • valve actuating member 52 is axially free of play between radial driving flanges 66 and 67 of the hollow shaft 37 via ball bearings 63 and 64, which impart smooth rotation of the hollow shaft 37 relative to the valve actuating member 52.
  • the electric drive motor 41 is driven by output signals from the electronic control unit 13 with that direction of rotation - the motor 41 can be driven in alternative directions of rotation - that its rotor 43 and with it the hollow shaft 37 - because of their thread engagement with the initially unoccupied spindle 39 - undergoes an axial displacement in the direction 28 opposite to the feed direction 27, which is also transmitted to the valve piston 34 of the follow-up control valve 12 via the valve actuating member 52, which also carries out this initial axial displacement of the hollow shaft 37, which thereby moves into its Function position I assigned to feed operation arrives. Due to the resulting - increasing - pressurization of the one drive pressure chamber 21 of the hydraulic motor 11, as shown in FIG.
  • the measuring system 14 for the explanation of which reference is now also made to the details of FIGS. 2a and 2b and 2c, comprises a total of 3, basically rotationally symmetrical encoder elements 68, 69 and 71, which can be seen from FIG. 1 Arrangement at an axial distance from one another in a rotationally and displaceably fixed manner are arranged on the end section 72 of the hollow shaft 37 which projects into the receiving space 51 of the measuring system 14.
  • So-called field plate sensors of a type known per se are used as sensor elements 74 and 75, in which the amplitudes of the output signals are independent of the rotational speed of the mechanical encoder elements 68, that is to say the signal level of their output signals varies between defined - upper and lower - extreme values, so that the output signals the level of the two sensor elements 74 and 75 can also be easily evaluated.
  • the gear-shaped transmitter element 68 and the annular flange-shaped transmitter element 69 and the associated electronic sensor elements 74 and 75 and 77 are arranged and designed so that the output signals of at least the two sensor elements 74 and 75 of the angular position measuring system 68, 74, 75 by the in operation possible axial displacements of the hollow shaft 37 - and thus also of the transmitter elements 68 and 69 - of the drive device 10 are not influenced, since the output signals of the two sensor elements 74 and 75 should also be able to be evaluated as precisely as possible with regard to the amounts of their amplitudes (signal level).
  • the simple design of the following error measuring system 71, 78 which can be seen in FIG. 1, has its mechanical encoder element 71 formed as an annular rib with conical flanks 79 and 81, which adjoin one another along a sharp ring edge 82, by their axial displacements relative to the sensor element 78 whose output signal level is influenced.
  • An element of the type is again provided as sensor element 78, as already explained for the angular position measuring system 68, 74, 75.
  • a position of the mechanical transmitter element 71 is linked to the - blocking - basic position O of the overrun control valve 12, in which the output signal of the sensor element 78 of the following error measuring system 71, 78 corresponds to a - high or low - extreme value, so that changes in the output signal level of the sensor element 78 are in each case monotonously related to the following error ⁇ S in one direction or the other.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Servomotors (AREA)
  • Control Of Position Or Direction (AREA)

Abstract

Un entraînement hydraulique pour les mouvements de réglage, d'avancement et de retour d'une tête d'outil d'une machine-outil comprend un moteur hydraulique (11) et une soupape de régulation par poursuite (12). La valeur de référence de la position est fixée et la valeur réelle indiquée en retour au moyen d'une broche filetée (39) et d'un écrou de broche (37) se présentant sous la forme d'un arbre creux. L'un de ces deux éléments peut être entraîné par un moteur électrique (41) afin d'établir la valeur de référence de la position. L'autre élément peut être entraîné afin d'indiquer en retour la valeur de la position réelle. Un système indicateur de position rotative et angulaire (68, 74, 75 et 69, 77) produit un signal de sortie qui mesure directement le nombre total de révolutions exécutées par l'arbre à valeur de référence prédéfinie ainsi que sa position azimutale à l'intérieur de chaque révolution. Un système détecteur de position électronique (71, 78 et 71', 78'; 71'') produit un signal de sortie qui mesure l'erreur de poursuite ΔS dont la position réelle de la tête d'outil ou de l'élément d'entraînement du moteur hydraulique (16) est en retard de phase par rapport à sa position de référence.

Claims (12)

  1. Dispositif de commande hydraulique (10) pour les mouvements d'approche et d'avancement ainsi que de retrait d'une tête porte-outil d'une machine-outil, comprenant
    a) un moteur hydraulique (11) muni d'un élément d'entraînement mobile (16, 19) solidaire de la tête porte-outil et pouvant être entraîné par une alternance d'alimentation en pression et de détente dans des volumes de pression d'entraînement (21, 22), et
    b) une soupape de réglage par poursuite (12) qui fonctionne avec une prédétermination de la valeur de position de consigne à commande électromécanique pour l'élément d'entraînement mobile (16) ainsi qu'avec une répétition mécanique de la valeur de position effective de ce dernier,
    c) pour la prédétermination de la valeur de position de consigne et pour la répétition de la valeur de position effective étant prévus une broche filetée (39) et un écrou de broche coopérant avec cette dernière et conformé en arbre creux (37), et l'un des deux éléments de ce système de broche-écrou pouvant être entraîné au moyen d'un moteur électrique (41), dans le sens de rotation de celui-ci, pour la prédétermination de la valeur de position de consigne, et l'autre (39) de ces deux éléments pouvant être déplacé par l'élément d'entraînement (16) dans le sens de la répétition de la valeur de position effective, et
    d) les signaux nécessaires pour la commande des mouvements du moteur électrique (41) étant générés par une unité de commande électronique (13) avec interface pour une commande NC ou CNC,
    caractérisé en ce qu'il comprend
    e) un système de détection de position angulaire (68, 74, 75, 69, 77) qui génère des signaux de sortie lesquels contiennent l'information sur le nombre de tours total effectué par l'élément de prédétermination de la valeur de consigne ainsi que sur la position azimutale de l'élément de prédétermination de la valeur de consigne (37) à l'intérieur de chaque tour, et
    f) un système de capteur de déplacement électronique (71, 78; 71', 78'; 71'') dont les signaux de sortie constituent un critère direct pour les déviations axiales de l'élément de prédétermination de la valeur de consigne (37) ainsi que d'un organe de manoeuvre (52) de la soupape de réglage par poursuite (12) qui suit ces déviations axiales à partir de sa position de repos, et donc un critère pour l'erreur de poursuite ΔS avec laquelle la position effective de la tête porte-outil et respectivement de l'élément d'entraînement (16) du moteur hydraulique (11) est en retard par rapport à sa position de consigne.
  2. Dispositif de commande hydraulique selon la revendication 1, caractérisé en ce qu'il utilise comme élément de prédétermination de la valeur de position de consigne, l'arbre creux (37) et comme élément de répétition de la valeur de position effective, la broche filetée (39).
  3. Dispositif de commande hydraulique selon la revendication 1 ou la revendication 2, caractérisé en ce qu'il comprend pour la commande du moteur électrique (41) dans le sens de la prédétermination de la valeur de position de consigne, une unité de commande et de traitement électronique (13) à laquelle peuvent également être transmis en tant que signaux d'entrée, les signaux de sortie du système de détection de position angulaire (68, 74, 75, 69, 77) ainsi que du système de capteur de déplacement (71, 78; 71', 78'; 71'', 78'') à partir du traitement desquels ladite unité de commande électronique (13) génère des signaux de correction pour une compensation au moins partielle de l'erreur de poursuite et/ou pour la stabilisation de l'erreur de poursuite ΔS et/ou pour la mise à l'arrêt du dispositif de commande (10) si l'erreur de poursuite ΔS dépasse une valeur de seuil réglable prédéterminée.
  4. Dispositif de commande selon l'une des revendications 1 à 3, caractérisé en ce que le système de mesure de position angulaire (68, 74, 75) comprend un élément capteur tournant (68) qui, vu dans le sens circonférentiel, présente un contour ondulé ou dentelé de manière périodique et dont le passage devant au moins un élément de détection (74 et/ou 75) génère les signaux de tension de sortie caractéristiques pour la position angulaire de l'élément de prédétermination de la valeur de consigne (37), et que cet élément capteur (68) est couplé coaxialement avec l'axe central (18) de l'élément de prédétermination de la valeur de consigne (37) et de l'élément de répétition de la valeur effective (37) et solidairement en rotation et en translation de l'élément de prédétermination de la valeur de consigne (37), tandis que l'élément de détection (74 et/ou 75) est solidaire de la machine et/ou qu'il est prévu un autre élément capteur (69) solidaire en rotation et en translation avec l'élément de prédétermination de la valeur de consigne (37), dont la circonférence ne présente qu'une saillie radiale (76') ou un évidement radial (76) dont le passage devant un élément de détection électronique supplémentaire (77) solidaire de la machine permet le déclenchement de signaux de référence pour le nombre des tours complets effectués par l'élément de prédétermination de la valeur de consigne (37)
  5. Dispositif de commande hydraulique selon l'une des revendications 1 à 4, caractérisé en ce que le système de capteur de déplacement (71, 78; 71', 78; 71'', 78', 78'') prévu pour la détermination des déviations axiales de l'élément de prédétermination de la valeur de position de consigne (37) de la soupape de réglage par poursuite (12) comprend un élément capteur (71; 71'; 71'') solidaire en rotation et en translation avec l'élément de prédétermination de la valeur de consigne (37), dont les déviations axiales par rapport à au moins un élément de détection électronique (78; 78' et/ou 78'') solidaire de la machine et répondant sans contact font varier le signal de sortie de ce dernier dans la mesure caractéristique de la déviation, et que le rotor (43) du moteur électrique (41) prévu pour la prédétermination de la valeur de position de consigne est couplé de manière solidaire en rotation et en translation avec l'élément de prédétermination de la valeur de consigne (37) et monté, conjointement avec celui-ci, de façon à pouvoir se déplacer axialement par rapport au stator (42) du moteur (41), qui est solidaire du carter.
  6. Dispositif de commande hydraulique selon l'une des revendications 1 à 5, utilisant comme élément de prédétermination de la valeur de position de consigne, l'arbre creux (37) et comme élément de position effective, la broche filetée (39) laquelle est couplée de manière rigide en translation avec l'élément d'entraînement (16) du moteur hydraulique (11), caractérisé en ce que la broche filetée (39) est entourée par l'arbre creux (37) sur une partie de sa longueur qui correspond au moins au déplacement de l'élément d'entraînement (16) du moteur hydraulique (11).
  7. Dispositif de commande hydraulique selon l'une des revendications 1 à 6, caractérisé en ce que le moteur électrique (41) prévu pour la commande de la prédétermination de la valeur de position de consigne est logé dans un volume d'huile de fuite (49, 51) du dispositif de commande (10).
  8. Dispositif de commande hydraulique selon la revendication 7, caractérisé en ce que le système de mesure de position angulaire (68, 74, 75, 69, 77) et/ou le système de mesure d'erreur de poursuite (71, 78; 71', 78', 71'', 78', 78'') sont, eux aussi, logés dans le volume d'huile de fuite (49, 51) du dispositif de commande (10).
  9. Dispositif de commande hydraulique selon l'une des revendications 1 à 8, caractérisé en ce que le système de mesure de position angulaire (68, 74, 75) comprend comme élément capteur mécanique, une couronne dentée (68) avec 100 dents (73) réparties à égales distances sur la circonférence de ladite couronne dentée et s'étendant dans le sens axial, qu'il est prévu deux éléments de détection électroniques (74 et 75) dont l'écartement azimutal Δφ est égal à un multiple impair d'un quart de la distance angulaire entre des dents (73) voisines de la couronne dentée (68), et que les deux éléments de détection électroniques (74 et 75) sont conformés en capteurs de la magnétorésistance d'un type bien connu en soi.
  10. Dispositif de commande hydraulique selon l'une des revendications 1 à 9, caractérisé en ce que l'élément capteur mécanique (71; 71'; 71'') du système de mesure d'erreur de poursuite présente au moins une surface de rampe (79 et/ou 81) qui s'étend en oblique par rapport à l'axe longitudinal central (18) dont la variation de la distance par rapport à l'élément de détection (78; 78', 78'') respectif liée au déplacement axial dudit élément capteur (71; 71'; 71''), conduit à une variation proportionnelle au déplacement du signal de sortie de l'élément de détection (78; 78', 78'') respectif.
  11. Dispositif de commande hydraulique selon la revendication 10, caractérisé en ce que l'élément capteur mécanique (71'') du système de mesure d'erreur de poursuite, vu sur sa longueur, présente un diamètre qui varie de manière périodique, et qu'il est prévu deux éléments de détection électroniques (78' et 78'') disposés l'un par rapport à l'autre à une distance axiale ΔL qui est égale à un multiple impair de 1/4, l désignant la longueur de périodicité de la variation du diamètre de l'élément capteur 71''.
  12. Dispositif de commande hydraulique selon l'une des revendications 1 à 11, caractérisé en ce que l'unité de commande électronique (13) comprend un circuit de correction et d'interprétation à l'aide duquel les signaux de sortie du système de mesure de position angulaire (68, 74, 75, 69, 77) et/ou du système de mesure d'erreur de poursuite (71, 78; 71', 78; 71'', 78', 78'') générés dans la position de base de la soupape de réglage par poursuite (12) peuvent être pris en compte comme valeurs de référence pour la mesure de la position angulaire et respectivement pour la mesure de l'erreur de poursuite.
EP90906855A 1989-05-07 1990-05-04 Entrainement hydraulique Expired - Lifetime EP0471695B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90906855T ATE93584T1 (de) 1989-05-07 1990-05-04 Hydraulische antriebsvorrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3914860 1989-05-07
DE3914860A DE3914860A1 (de) 1989-05-07 1989-05-07 Hydraulische antriebsvorrichtung

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EP0471695A1 EP0471695A1 (fr) 1992-02-26
EP0471695B1 true EP0471695B1 (fr) 1993-08-25

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EP90906855A Expired - Lifetime EP0471695B1 (fr) 1989-05-07 1990-05-04 Entrainement hydraulique

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US (1) US5192174A (fr)
EP (1) EP0471695B1 (fr)
JP (1) JPH04507066A (fr)
DE (2) DE3914860A1 (fr)
WO (1) WO1990013747A1 (fr)

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WO1995020781A1 (fr) * 1994-01-27 1995-08-03 Hr Textron Inc. Servodistributeur a actionnement direct ayant un detecteur de position du moteur

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DE4331033C1 (de) * 1993-09-13 1995-03-09 Grundig Ag Prüfeinrichtung zur Abstechkontrolle bei Stangendrehautomaten
FI102413B (fi) * 1996-04-11 1998-11-30 Lako Forest Oy Järjestelmä hydraulisylinterin käyttämän laitteen työliikkeen seuraami seksi
US6494617B1 (en) 1999-04-30 2002-12-17 General Electric Company Status detection apparatus and method for fluid-filled electrical equipment
US6401518B1 (en) 1999-07-29 2002-06-11 General Electric Company Fluid filled electrical device with diagnostic sensor located in fluid circulation flow path
US6865498B2 (en) * 2001-11-30 2005-03-08 Thermwood Corporation System for calibrating the axes on a computer numeric controlled machining system and method thereof
GB2405933A (en) * 2003-09-12 2005-03-16 Page Aerospace Ltd Measuring movement of a hydraulic actuator
KR100609631B1 (ko) * 2004-01-12 2006-08-08 인하대학교 산학협력단 복합 베어링이 구비된 일체형 에어 스핀들 시스템
AT504536B1 (de) 2006-10-30 2009-03-15 Ehrenleitner Franz Verfahren zur bewegung von lasten, werkzeugen und dergleichen
EP2577259A1 (fr) * 2010-05-28 2013-04-10 E.I. Du Pont De Nemours And Company Procédé pour produire des zones d'essai standardisées sur des revêtements organiques

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Also Published As

Publication number Publication date
WO1990013747A1 (fr) 1990-11-15
DE59002490D1 (de) 1993-09-30
EP0471695A1 (fr) 1992-02-26
DE3914860A1 (de) 1990-11-08
JPH04507066A (ja) 1992-12-10
US5192174A (en) 1993-03-09

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