WO1997014895A1 - Actionneur lineaire - Google Patents

Actionneur lineaire Download PDF

Info

Publication number
WO1997014895A1
WO1997014895A1 PCT/NL1996/000402 NL9600402W WO9714895A1 WO 1997014895 A1 WO1997014895 A1 WO 1997014895A1 NL 9600402 W NL9600402 W NL 9600402W WO 9714895 A1 WO9714895 A1 WO 9714895A1
Authority
WO
WIPO (PCT)
Prior art keywords
translation
coupling member
rotational
displacement
setting device
Prior art date
Application number
PCT/NL1996/000402
Other languages
English (en)
Inventor
Stefan Frits Brouwer
Original Assignee
Iku Holding Montfoort B.V.
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 Iku Holding Montfoort B.V. filed Critical Iku Holding Montfoort B.V.
Priority to AU72289/96A priority Critical patent/AU7228996A/en
Publication of WO1997014895A1 publication Critical patent/WO1997014895A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/2018—Screw mechanisms with both screw and nut being driven, i.e. screw and nut are both rotating
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60R—VEHICLES, VEHICLE FITTINGS, OR VEHICLE PARTS, NOT OTHERWISE PROVIDED FOR
    • B60R1/00—Optical viewing arrangements; Real-time viewing arrangements for drivers or passengers using optical image capturing systems, e.g. cameras or video systems specially adapted for use in or on vehicles
    • B60R1/02—Rear-view mirror arrangements
    • B60R1/06—Rear-view mirror arrangements mounted on vehicle exterior
    • B60R1/062—Rear-view mirror arrangements mounted on vehicle exterior with remote control for adjusting position
    • B60R1/07—Rear-view mirror arrangements mounted on vehicle exterior with remote control for adjusting position by electrically powered actuators
    • B60R1/072—Rear-view mirror arrangements mounted on vehicle exterior with remote control for adjusting position by electrically powered actuators for adjusting the mirror relative to its housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H2025/2062—Arrangements for driving the actuator
    • F16H2025/2081—Parallel arrangement of drive motor to screw axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H2025/2062—Arrangements for driving the actuator
    • F16H2025/209—Arrangements for driving the actuator using worm gears

Definitions

  • " ⁇ "displacement setting device is generally known, tor instance from EP-A- 0 1 70 .296, and is eminently suitable for being used as ac t uator in an electrically remote-adjustable mirror for. for ins t ance, motor vehicles.
  • the invention w i ll herein b elow b e discussed within the framework of the use i n a wing mirror for a mo t orcar, but it is emphasized that the invention is no t limited to such use.
  • the inven t ion is in principle applicable in any field of t echnology w h ere there is a need for effecting , by means of a motor, a linear movement of a part whose linear pos i tron should b e set in an accurate manner.
  • the translation output member to be linearly displaced generally has the form of a bar prov i ded with an external screw thread.
  • th i s par t w i ll therefore be referred to as screw bar.
  • the screw b ar is dispose d in a frame part which permits axial displacement of the screw bar but prevents rotation thereof .
  • the screw thread of the screw bar is in engagement with a dr i ving part wh i ch b ears a gear ring ex t ernally and which can rotate relat i ve to the frame but cannot perform an axial displacement , when that driving part is rotated, for instance by an elec t romotor, the screw b ar, which cannot rotate along with that gear wheel on account of its being restrained from rotation b y that frame part is forced to move axially relative to the frame.
  • the device according to the invention has the combination of the features as described in claim 1.
  • Fig. IA schematically shows a conventional displacement setting device
  • Fig. IB is a section taken on the line B-B in Fig. IA;
  • Fig. 2A schematically shows a displacement setting device according to the present invention in accordance with the line
  • Fig. 2B is a schematic section of a translation coupling member taken on the line B-B in Fig. 2A;
  • FIGs. 3A-3F schematically illustrate embodiments of a displacement setting device according to the present invention, in each case with a common driving source;
  • Fig. 4 schematically illustrates an embodiment of a displacement setting device according to the present invention, with individual driving sources
  • Fig. 5 schematically illustrates a variant of the displacement setting device shown in Fig. 4;
  • Fig. 6A shows, to a larger scale, a detail of a coupling member of an embodiment of the variant illustrated in Fig. 5;
  • Fig. 6B is a cross section of a portion of an embodiment of the variant illustrated in Fig. 5, to show a detail thereof;
  • Fig. 6C is a cross section comparable with Fig. 6B, of a portion of another variant.
  • identical or comparable parts will be designated by the same reference numerals.
  • Fig. l schematically illustrates the operation of a conventional displacement setting device l, such as it is for instance known from the above-cited EP-A-O,170,296.
  • This displacement setting device l essentially comprises two parts, viz. a translation output member 10 and rotational input means 20, which parts are arranged in a frame 2, and wherein rotation-restraining means 30 are provided.
  • the translation output member 10 can perform a translation relative to that frame 2 in a direction indicated by an arrow 3.
  • the known translation output member 10 generally has the shape of a round screw bar whose length direction is oriented according to the translation direction 3, and has a screw thread 11 on an outside surface 12 thereof.
  • the translation Output member 10 comprises, at an end 13 thereof, means 14 for engagement with a mirror supporting plate, not shown, which means 14 can for isntance comprise a ball which can form part of a ball joint.
  • the rotational input means 20 comprise a rotational coupling member 21, arranged in the frame 2 for rotation about an axis of rotation 4 so that an axial displacement of the rotational coupling member 20 relative to the frame 2 in the direction 3 is prevented.
  • the rotational coupling member 21 and the screw bar 10 can rotate relative to each other.
  • the rotational coupling member 21 has the form of a gear wheal that is rotatable in the frame 2 and positioned coaxially relative to the screw bar 10, and provided with an internal screw thread 22 engaging the external screw thread 11 of the screw bar 10.
  • the rotation-restraining means 30 serve to limit the freedom of movement of the screw bar 10 relative to the frame 2 to an axial translation.
  • the known rotation-restraining means 30 comprise a projection 31 which is rigidly fixed relative to the frame 2 and engages a longitudinal groove 15 formed in the outside surface 12 of the screw bar 10. That projection 31 can be an integral part of the frame 2.
  • the screw bar 10 can perform a translation relative to the frame 2 in the direction 3, and the rotation- restraining means 30 provide that the rotation of the screw bar 10 relative to the frame 2 is restrained.
  • the gear wheel 21 is driven for rotation by means of an electromotor which, for the sake of simplicity, is not shown, with the interposition of a transmission system which, for the sake of simplicity, is not shown either.
  • the screw bar 10 incapable of rotating along with that gear wheel 21 owing to its being restrained from rotation by the rotation-restraining means 30, is forced to move axially relative to the gear wheel 21, and hence in the direction 3 relative to the frame 2.
  • the axial translation speed V of the screw bar 10 is proportional to the absolute rotational speed ⁇ 2 ⁇ of the gear wheel 21 according to the formula v ⁇ S-to 2 ⁇ .
  • Fig. 2A schematically illustrates a displacement setting device 100 according to the invention.
  • This displacement setting device 100 essentially comprises three parts, viz. a translation output member 110, first rotational input means 120, and second rotational input means 130, which parts are arranged in a frame 2.
  • the translation output member 110 can be identical to the known translation output member 10 discussed with reference to Fig. 1, for which reason the translation output member 110 will hereinbelow again be referred to as screw bar.
  • the screw bar 110 has been changed to the extend that the longitudinal groove 15 is replaced by a flattened surface part 16, which is actually easier to provide than a groove.
  • the first rotational input means 120 comprise a rotational coupling member 121, which can be identical to the gear wheel 21 discussed with reference to Fig. l.
  • the second roational input means 130 comprise a translation coupling member 131, which, like the rotational coupling member 121, is arranged in the frame 2 for rotation so that an axial displacement of the translation coupling member 131 relative to the frame 2 in the direction 3 is prevented.
  • the translation coupling member 131 is arranged so as to be coaxial to the screw bar 10.
  • the displacement setting device 100 further comprises rotation-restraining means 140 which restrain the translation coupling member 131 and the screw bar 110 from rotating relative to each other, i.e. prevent a mutual rotation between the translation coupling member 131 and the screw bar 110, while those rotation- restraining means 140 permit a mutual axial displacement between the translation coupling member 131 and the screw bar 110 in the direction 3.
  • the translation coupling member 131 has the form of a second gear wheel, and those rotation-restraining means 140 comprise the flattened surface parts 16 of the screw bar 110 and a central hole 132 in the second gear wheel 131 whose contour corresponds to the contour of the screw bar 110.
  • the displacement setting device 100 thus has two rotational inputs 120 and 130, and an axial displacement of the translation output member (screw bar) 110 relative to the frame 2 takes place if the two rotational inputs 120 and 130 are driven at different rotational speeds, the axial displacement speed v of the translation output member 110 relative to the frame 2 being on the one hand proportional to the pitch S of the screw thread 11, and being on the other hand proportional to the difference between the rotational speeds ⁇ i2 ⁇ and ⁇ 131 of the rotational coupling member 121 and the translation coupling member 131 respectively according to the formula v ⁇ S- ( ⁇ i2 ⁇ - ⁇ i3i ) .
  • the second rotational input means 130 are held stationary relative to the frame 2, while the first rotational input means 120 are driven.
  • the displacement setting device 100 then behaves in the same manner as the displacement setting device 1 discussed with reference to Fig. 1, so that the detailed discussion thereof need not be repeated.
  • the displacement direction of the screw bar 110 that results when the second rotational input means 130 are held stationary while the first gear wheel 121 is rotated clockwise, as viewed from the bottom side in Fig. 2A, will be referred to as positive displacement direction.
  • the first rotational input means 120 are held stationary, while the second rotational input means 130 are driven.
  • the screw bar 110 is then rotated relative to the stationary first gear wheel 121, and forced, by the intermeshing screw threads 11 and 22, to move axially.
  • the second gear wheel 131 is rotated through 360°, the translation path travelled by the screw bar 110 is equal to the pitch of the screw thread 11.
  • a clockwise rotation of the second gear wheel 131 as viewed from the bottom side in Fig.
  • the first rotational input means 120 and the second rotational input means 130 are both driven, in such a manner that the two gear wheels 121 and 131 are rotated in the same direction at the same rotational speed.
  • the screw bar 110 rotates along with these two gear wheels at the same rotational speed. Accordingly, the three parts 110, 121 and 131 behave like one whole, and the screw bar 110 will undergo no axial displacement.
  • the first rotational input means 120 and the second rotational input means 130 are both driven, in such a manner that the two gear wheels 121 and 131 are rotated at rotational speeds that differ as to direction and/or magnitude.
  • the direction and speed of displacement of the screw bar 110 can be described as a linear combination of, on the one hand, the displacement caused by rotation of the first gear wheel 121 with a supposedly stationary second gear wheel 131, and, on the other hand, the displacement caused by rotation of the second gear wheel 131 with a supposedly stationary first gear wheel 121.
  • the axial displacement speed v of the translation output member 110 relative to the frame 2 meets the formula v ⁇ S-itom - ⁇ i3 ⁇ ) .
  • this can be utilized by driving the two rotational input means 120 and 130 at relatively high rotational speeds that differ slightly relative to each other, as a result of which the screw bar 110 is displaced at a relatively low translation speed.
  • Fig. 2A it is shown that the rotational coupling member 121 and the translation coupling member 131 can be individually arranged in the frame, by which it is meant that each of these coupling members has its axial main faces contacting frame portions.
  • a coupling member 121, 131 When a coupling member 121, 131 is rotated, those axial main faces will have sliding contact with those frame portions, and the inevitable friction will mean a loss of power.
  • This loss is substantially proportional to the rotational speed of each coupling member 121, 131.
  • it is possible to reduce this friction and this loss of power by placing the rotational coupling member 121 and the translation coupling member 131 one against the other, i.e. without a frame portion in between.
  • the two rotational input members 120 and 130 are driven from a common source (such as an electromotor) with the interposition of transmission means 150, the ratio of transmission from those transmission means 150 to the first rotational input 120 differing from the ratio of transmission from those transmission means 150 to the second rotational input 130.
  • a common source such as an electromotor
  • Figs. 3A-F illustrate examples thereof, while, for simplity's sake, the frame 2 is not shown.
  • the rotational coupling member 121 and the translation coupling member 131 are designed as gear wheels, and the transmission means 150 comprise two driving gear wheels 151 and 152 which are in engagement with the gear wheels 121 and 131 respectively.
  • the driving gear wheels 151 and 152 can be mounted on a common shaft 153, and can be manufactured as a single, integral part.
  • the above- mentioned differences in the ratios of transmission can be caused by a difference between the number of teeth of the first gear wheel 121 and the number of teeth of the second gear wheel 131, and/or by a difference between the number of teeth of the first driving gear wheel 151 and the number of teeth of the second driving gear wheel 152.
  • the driving gear wheels 151 and 152 are replaced by a pinion 154, with the two gear wheels 121 and 131 having mutually different numbers of teeth. That difference is preferably equal to one.
  • the two gear wheels 121 and 131 can be designed as conical gear wheels.
  • the driving gear wheels 151 and 152 can likewise be designed as conical gear wheels and positioned in a configuration as sketched in Fig. 3A.
  • the conical wheels 121 and 131 are positioned so that they lie on a common conical plane, so that they can be driven by a single pinion 154 or by a single conical gear wheel 155 respectively.
  • the rotational coupling member 121 and the translation coupling member 131 are friction wheels, which, by means of a friction coupling, are driven by friction wheels or a common friction pinion or a common friction bevel gear.
  • the driving friction pinion can be replaced by a friction bevel gear having an oblique axis of rotation.
  • the difference in rotational speeds is no longer dependent on the difference in numbers of teeth, which is always a discrete number, but on the apex angle of the cone describing the surfaces of the conical friction wheels, which angle can, in principle, be selected freely within a large angular range.
  • the rotational coupling member 121 and the translation coupling member 131 are designed as worm wheels, and the transmission means 150 comprise a common worm 156 driving the two worm wheels 121 and 131.
  • the number of teeth of the first worm wheel 121 differs from the number of teeth of the second worm wheel 131, which difference is for instance equal to one.
  • Fig. 3F illustrates this for an embodiment derived from the embodiment of Fig. 3E, wherein the rotational coupling member 121 and the translation coupling member 131 are designed as gear wheels or worm wheels driven by a first worm 161 and a second worm 162 respectively.
  • the first worm 161 is mounted on a first worm shaft 163 on which a first driving gear wheel 164 is mounted as well.
  • the second worm 162 is mounted on a second worm shaft 165 with a second driving gear wheel 166.
  • the two driving gear wheels 164 and 166 are driven by a common gear wheel 167.
  • the driving gear wheels 164 and 166 can have mutually different numbers of teeth and/or the two worm wheels 121 and 131 can have mutually different numbers of teeth.
  • the two rotational input members 120 and 130 are individually driven from different sources (such as two electromotors Ml and M2) with the interposition of transmission means 170 and 180 respectively.
  • Fig. 4 wherein, for simplicity's sake, the frame 2 is not shown, schematically illustrates an example thereof, the rotational coupling member 121 and the translation coupling member 131 being designed as gear wheels or worm wheels driven by a first worm 171 and a second worm 181 respectively.
  • the gear wheels or worm wheels 121 and 131 can have mutually equal numbers of teeth, the worms 171 and 181 can be identical, the motors Ml and M2 can be identical, and further parts, if any, of the transmission means 170 and 180 can be mutually identical. Differences in rotational speeds of the gear wheels or worm wheels 121 and 131 can be effected by energizing the two motors Ml and M2 with mutually different driving voltages VI and V2, which can each by themselves be virtually equal to the nominal operating voltage V N of the motors, so that substantially the full power of those motors is available.
  • an advantage of such an embodiment is that, during operation, these driving voltages VI and V2 can be varied in order to vary the axial displacement speed of the translation output member 10.
  • the second driving voltage V2 is then increased, causing the displacement speed v to decrease, while the force that can be exerted by the translation output member 10 remains maximal.
  • the second driving voltage V2 will be virtually equal to the first driving voltage Vi, so that the translation output member 10 is moved slowly and extremely accurately towards its intended position, while much force can be exerted.
  • a slow displacement of the translation output member can only be effected by causing the driving motor to rotate at low speed, as a consequence of which relatively little power is available.
  • the driving voltages VI and V2 can be provided by a control device 190 on the basis of a control signal 191 to be entered by a user.
  • Fig. 5 wherein, for simplicity's sake, the frame 2 is not shown, schematically illustrates another example of this structural variant, with the rotational coupling member 121 and the translation coupling member 131 again being designed as gear wheels or worm wheels driven by a first worm 171 and a second worm 181 respectively.
  • the rotational coupling member 121 and the translation coupling member 131 have mutually different diameters and mutually different numbers of teeth; in the example shown, the diameter of the rotational coupling member 121 is larger than that of the translation coupling member 131.
  • the worms 171 and 181 are driven from two different motors Ml and M2 (cf. Fig. 4), and can be directly mounted on the output shaft of the respective motor; for the sake of simplicity, this is not shown in Fig. 5.
  • the worms 171 and 181 can be mutually identical.
  • the displacement setting device of Fig. 5, which is generally designated by the reference numeral 200, is useful in particular for applications wherein it is desired to be able to displace a translation output member 110 at two different speeds, in order that a part to be set can be selectively set at two different speeds.
  • An example of a practical application in respect of which such a desire is relevant, is a wing mirror of a vehicle such as a motorcar.
  • the displacement setting device 200 has a first switch Si, switching the first motor Ml ON/OFF in a desired rotational direction, while the second motor S2 remains stationary, so that the coupling member having the smallest diameter (131) is held still.
  • the rotation of the coupling member having the largest diameter (121) brings about a relatively slow displacement of the translation output member 110 in the manner described hereinabove.
  • the part to be set is quickly moved from that set position into a different position, and that, afer that, it is quickly returned into the above-mentioned set position again.
  • An example of such a case is the driving a car backwards, for which it can be desired to direct the mirror downwards to enable the driver to see the road surface and the curb alongside the vehicle.
  • the displacement from the normal operating position into the drive-backwards position and back takes place relatively quickly, and that on the other hand, it is desired that when the mirror is being repositioned, it precisely returns to the normal operating position, i.e. the position wherein the mirror was previously set.
  • the adjusting device has a second switch S2, which switches the second motor M2 ON/OFF in a desired rotational direction, while the first motor Ml remains stationary, so that the coupling member having the largest diameter (121) is held still.
  • the rotation of the coupling member having the smallest diameter (131) brings about a relatively quick displacement of the translation output member 110 in the manner described hereinabove.
  • Such an operation with an accurate setting mode of a relatively slow displacement speed and a quick setting mode of a relatively high displacement speed can also be realized in a particularly simple manner with the embodiment as described with reference to Fig. 4, i.e. the gear wheels 121 and 131 can in principle be equal to each other.
  • the gear wheel 121 is driven at a first, substantially constant rotational speed ⁇ i2 ⁇ , and the other gear wheel 131 is driven at a second, substantially constant speed ⁇ i3 ⁇ .
  • These two rotational speeds differ from each other slightly, i.e. I ⁇ i2 ⁇ - ⁇ i3i l > 0.
  • This can be achieved by causing the driving voltages VI and V2 for the motors Ml and M2 to differ from each other slightly, while the numbers of teeth of the gear wheels 121 and 131 can then be equal to each other, and the worms 171 and 181 can be equal to each other.
  • these driving voltages VI and V2 can be substantially equal to each other, but the ratio of transmission from the motor Ml to the gear wheel 121 can differ from the ratio of transmission from the motor M2 to the gear wheel 131, for instance because the gear wheels 121 and 131 have different numbers of teeth. Preferably, the difference in teeth numbers is equal to l.
  • the change-over from the accurate setting mode with relatively low displacement speed to the quick setting mode with relatively high displacement speed is in this case effected by changing the sign of one of the above-mentioned driving voltages, for instance V2. Referring to the above-mentioned formula V ⁇ S- ( ⁇ i i - ⁇ i3 ⁇ ) in the accurate setting mode, the relatively low displacement speed V- can then be written as
  • the slow mode is defined through energization of the first motor Ml only, so that the displacement speed is then defined by and that the quick mode is defined through energization of both motors Ml and M2, so that the displacement speed is then defined by
  • Such angle-limiting means 210 for the coupling member of the smallest diameter (131) can be provided in different manners.
  • the second motor M2 can be a stepping motor, and when the mirror is being repositioned from the drive-backwards position into the normal operating position, the motor M2 is rotated backwards through as many steps as the number of steps through which the motor M2 was rotated for displacing the mirror from the normal operating position into the drive-backwards position.
  • a rotational-angle detector can be connected to the output shaft of the motor M2, for instance a detector of the type which comprises sectors whose passage can be counted by means of a Hall-sensor.
  • FIG. 6A is a bottom view of the coupling member 131, and shows that in a main face 211 of the coupling member 131, a circumferential groove 212 is formed.
  • the circumferential groove 212 has two ends 213 an 214, and has, throughout its Length, the same distance R to the center of rotation of the coupling member 131.
  • Connected to the frame 2 is a stop pin 215, reaching into the circumferential groove 212, as sketched in the cross section of Fig. 6A.
  • the stop pin 215 moves through the length of the circumferential groove 212.
  • the stop pin 215 reaches an end 213 or 214 of the circumferential groove 212, further rotation of the coupling member 131 is prevented.
  • the stop pin 215 rests against one of the ends 213, 214 of the circumferential groove 212. Only when the mirror is moved into the drive-backwards position through operation of the second switch S2 does the coupling member 131 rotate, until the stop pin 215 reaches the other one of the ends 213, 214 of the circumferential groove 212, whereby further rotation of the coupling member 131 is prevented.
  • the drive-backwards position is defined through the cooperation of the stop pin 215 and the other one of the ends 213, 214 of the circum erential groove 212.
  • the coupling member 131 rotates in the other direction until the stop pin 215 reaches again the above- mentioned one end of the circumferential groove 212. In this manner, the normal operating position is defined with a good reproducibility through the cooperation of the stop pin 215 and the above-mentioned one end of the circumferential groove 212.
  • the displacement turn between the normal operating position and the drive-backwards position is defined by the angular distance between the two ends 213 and 214 of the circumferential groove 212, which angular distance will, in the embodiment discussed hereinabove, be less than 360°. If it is desired and/or necessary that the rotational turn of the coupling member 131 be greater than
  • the stop pin 215 should then have a freedom of radial displacement in order that the spiral-shaped groove can be followed from the beginning to the end, comparable with the needle of a record player.
  • the stop pin 215 can for instance be designed as a ball 215', and the freedom of radial displacement can be provided by positioning the ball in a radially directed groove 216 formed in the frame 2, as schematically illustrated in Fig. 6C, rather than fixedly connecting the ball to the frame 2.
  • the translation output member is a screwed bush having an internal screw thread, with the rotational coupling member then comprising coupling means for engaging that internal screw thread.
  • the means for restraining rotation relative to the translation coupling member can then comprise an unround profile of the outside contour of the translation output member.
  • the translation output member is hollow and internally provided with means such as, for instance, a non-central and/or non-round hole for restraining rotation relative to a central pin with matching contour of the translation coupling member.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Multimedia (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention porte sur un dispositif d'ajustement de déplacement (100) permettant de convertir un mouvement de rotation en mouvement de translation qui comporte, d'une part, un élément de sortie (110) à même d'exécuter une translation par rapport à un bâti (2) et, d'autre part, deux organes d'entrée en rotation (120, 130), comprenant un élément de couplage rotatif (121) et un élément de couplage translationnel (131), respectivement, ces éléments de couplage (121, 131) étant montés rotatifs dans le bâti de manière que leur déplacement axial par rapport à celui-ci soit impossible. L'élément de sortie à translation (110) peut exécuter un mouvement combiné rotatif - translationnel par rapport à l'élément de couplage rotatif (121). Des organes de couplage (11, 22) convertissent une rotation réciproque relative en translation réciproque relative. L'élément de sortie à translation (110) est à même d'exécuter un mouvement de translation, mais non de rotation, par rapport à l'élément de couplage translationnel (131). La vitesse de translation de l'élément de sortie à translation (110) est proportionnelle à la différence entre les vitesses de rotation des deux éléments de couplage (121, 131).
PCT/NL1996/000402 1995-10-17 1996-10-17 Actionneur lineaire WO1997014895A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU72289/96A AU7228996A (en) 1995-10-17 1996-10-17 Linear actuator

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NL1001436A NL1001436C2 (nl) 1995-10-17 1995-10-17 Verplaatsingsinstelinrichting.
NL1001436 1995-10-17

Publications (1)

Publication Number Publication Date
WO1997014895A1 true WO1997014895A1 (fr) 1997-04-24

Family

ID=19761713

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/NL1996/000402 WO1997014895A1 (fr) 1995-10-17 1996-10-17 Actionneur lineaire

Country Status (3)

Country Link
AU (1) AU7228996A (fr)
NL (1) NL1001436C2 (fr)
WO (1) WO1997014895A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2892789A1 (fr) * 2005-10-27 2007-05-04 Renault Sas Actionneur de passage de vitesses pour boite de vitesses robotisee.

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3015528A1 (de) * 1980-04-23 1981-10-29 Unitechnic AG, Chur Stelltrieb fuer rueckblickspiegel, fenster, scheinwerfer o.dgl. teile bei fahrzeugen
CH653755B (fr) * 1981-12-10 1986-01-15
GB2202607A (en) * 1987-03-18 1988-09-28 Hiroshi Teramachi Composite motion guiding unit comprising a ball screw and ball spline
EP0528418A1 (fr) * 1991-08-19 1993-02-24 Ichikoh Industries Limited Mirroir à commande à distance électrique

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3015528A1 (de) * 1980-04-23 1981-10-29 Unitechnic AG, Chur Stelltrieb fuer rueckblickspiegel, fenster, scheinwerfer o.dgl. teile bei fahrzeugen
CH653755B (fr) * 1981-12-10 1986-01-15
GB2202607A (en) * 1987-03-18 1988-09-28 Hiroshi Teramachi Composite motion guiding unit comprising a ball screw and ball spline
EP0528418A1 (fr) * 1991-08-19 1993-02-24 Ichikoh Industries Limited Mirroir à commande à distance électrique

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2892789A1 (fr) * 2005-10-27 2007-05-04 Renault Sas Actionneur de passage de vitesses pour boite de vitesses robotisee.

Also Published As

Publication number Publication date
NL1001436C2 (nl) 1997-04-22
AU7228996A (en) 1997-05-07

Similar Documents

Publication Publication Date Title
US3396600A (en) Power operated tilt and telescope steering assembly
KR100465005B1 (ko) 자동차핸들축장치
US5231473A (en) Lens barrel
EP1542342B1 (fr) Generateur de moteur et vehicule a moteur electrique
US4612822A (en) Tilt steering equipment
EP1255661A1 (fr) Mecanisme d'inclinaison lineaire avec logement en plastique
EP0896917B1 (fr) Dispositif de direction assistee
CN1065712A (zh) 小型直线驱动器
JP3592508B2 (ja) ステッピングモータ、光軸調整装置及び移動範囲設定方法
NL2021341B1 (nl) Actuator
JPS60154955A (ja) 電動式動力舵取り装置
WO1997014895A1 (fr) Actionneur lineaire
GB2025598A (en) Device for adjusting the headlamps of a motor vehicle
JPS6283246A (ja) テレスコピツクステアリング装置
EP0269081B1 (fr) Dispositif de support pour un élément de miroir de rétroviseur
EP0614783A1 (fr) Dispositif de réglage de l'orientation d'un miroir pour rétroviseurs
KR20050008354A (ko) 스티어링휠의 틸팅 및 텔레스코픽 장치
JPS5863532A (ja) ヘツドランプ傾動装置
JPH09281378A (ja) 表面波モータ内蔵レンズ鏡筒
JPH08295247A (ja) ステアリング機構
JP2593815Y2 (ja) 電動リモコンミラーの角度変位制御装置
JP3994780B2 (ja) 車両用操舵制御装置
JPH0529134A (ja) 電動式リニアアクチユエータ
JPH0226086Y2 (fr)
JP2519688Y2 (ja) 電動式リモートコントロールミラー

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AL AM AT AU AZ BA BB BG BR BY CA CH CN CU CZ DE DK EE ES FI GB GE HU IL IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MD MG MK MN MW MX NO NZ PL PT RO RU SD SE SG SI SK TJ TM TR TT UA UG US UZ VN AM AZ BY KG KZ MD RU TJ TM

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): KE LS MW SD SZ UG AT BE CH DE DK ES FI FR GB GR IE IT LU MC NL PT SE BF BJ CF CG

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
121 Ep: the epo has been informed by wipo that ep was designated in this application
REG Reference to national code

Ref country code: DE

Ref legal event code: 8642

NENP Non-entry into the national phase

Ref country code: JP

Ref document number: 97515709

Format of ref document f/p: F

122 Ep: pct application non-entry in european phase
NENP Non-entry into the national phase

Ref country code: CA