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WO2024255941A1 - Actionneur pour fournir un couple, ledit actionneur comprenant un entraînement linéaire - Google Patents

Actionneur pour fournir un couple, ledit actionneur comprenant un entraînement linéaire Download PDF

Info

Publication number
WO2024255941A1
WO2024255941A1 PCT/DE2024/100163 DE2024100163W WO2024255941A1 WO 2024255941 A1 WO2024255941 A1 WO 2024255941A1 DE 2024100163 W DE2024100163 W DE 2024100163W WO 2024255941 A1 WO2024255941 A1 WO 2024255941A1
Authority
WO
WIPO (PCT)
Prior art keywords
lever
movement
linear drive
connection point
coupling element
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.)
Pending
Application number
PCT/DE2024/100163
Other languages
German (de)
English (en)
Inventor
Peter Greb
Laszlo Man
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of WO2024255941A1 publication Critical patent/WO2024255941A1/fr
Anticipated expiration legal-status Critical
Pending legal-status Critical Current

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
    • F16H21/00—Gearings comprising primarily only links or levers, with or without slides
    • F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
    • F16H21/44—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for conveying or interconverting oscillating or reciprocating motions
    • 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

Definitions

  • the present invention relates to an actuator for providing a torque with a linear drive and a gear for converting a linear movement into a rotary movement, wherein the gear comprises a lever which rotary drives a shaft to be subjected to the torque.
  • Such actuators are already known from DE 10 2016 207 827 A1 with a non-linear actuation force for an actuation unit for an automatic transmission (preferably a PRND automatic transmission system) of a motor vehicle.
  • a corresponding slide track is provided to generate the non-linearity.
  • An actuator preferably for a clutch actuation with an articulated transmission between a linear gear and a shaft is known from WO 2015 070 850 A1.
  • the present invention has the object of providing a generic actuator with a non-linear characteristic curve in a simple manner.
  • the gear of the actuator further comprises a coupling element which is connected to the linear drive via a first connection point and to the lever via a second connection point, so that energy is transferred between the linear drive and the lever exclusively via the coupling element, and the coupling element is rotatably mounted in both connection points.
  • the coupling element provides a third component that connects them, which can be used in a particularly simple manner can be mounted and enables a non-linear characteristic of the actuator through a corresponding energy transfer from the linear drive to the lever and thus to the shaft.
  • the lever is connected to the shaft at a second lever end via a third connection point in a rotationally fixed manner and to the coupling element at a first lever end via the second connection point in a rotationally fixed manner, and the lever creates a rigid connection between the two connection points.
  • the non-linearity of the actuator can be easily adjusted by adjusting the positions of the connection points and the length of the coupling element, since it is not the distance of the second lever end from the shaft that can be varied, only the transmitted torque or the corresponding rotational speed.
  • the movement of the lever in space is defined by the position of the third connection point fixed to the housing as a constraint, and the rotational speed and torque of the shaft are determined by the length of the coupling element in conjunction with its position on the linear drive.
  • the coupling element creates a rigid connection between the first and second connection points, so that a linear movement of the first connection point by the linear drive results in a first pivoting movement of the second connection point about the first connection point, as well as in a second pivoting movement of the second connection point about the third connection point, so that due to the rotationally fixed connection of the lever to the shaft, the second pivoting movement causes a rotation of the shaft.
  • the path covered by the second connection point is predetermined by the constraint of the rigid lever.
  • the non-linearity of the rotational speed or the transmitted torque is predetermined by the corresponding superposition of the two pivots to form a fixed curve.
  • the invention also provides that the coupling element connects the lever and the linear drive to one another in such a way that the second connection point is moved along a trajectory, so that in a first working area around a first end point of the trajectory, a movement of the first connection point by the linear drive is translated into a first rotational movement of the shaft and in a second working range around a second end point a movement of the first connection point is reduced by the linear drive into a second rotational movement of the shaft, whereby the first rotational movement covers a larger angular range with a smaller force transmission in a time interval than the second rotational movement.
  • certain working points and a transition area between them for the actuating force of the shaft can be defined, which correspond to a desired non-linearity of the actuation and merge into one another.
  • the coupling element in the second end point the coupling element is aligned perpendicular to the lever and the movement axis of the linear drive and the lever is aligned parallel to the movement axis.
  • the force acting from the linear drive on the coupling element acts perpendicular to the tangent of the circular arc described by the second end of the lever, the transmitted torque is very small, and a high rotational speed can be achieved accordingly.
  • the actuator is also self-locking. This is even more true when friction points on the actuator are taken into account.
  • the coupling element is aligned parallel to the movement axis of the linear drive and perpendicular to the lever at the first end point. This results in a maximum torque and a minimum rotational speed. Accordingly, a stable position of the actuator is also provided here.
  • a first, preferably housing-fixed stop is provided in the first end point for fixing the first end point and/or a second, preferably housing-fixed stop is provided in the second end point for fixing the second end point, and wherein the second lever end is designed to stop the lever against the first and/or second stop.
  • the stops can be provided, for example, as an extension of a spindle of the linear drive on an actuator housing and in the opposite end position as a stop for the lever.
  • first and/or second stop is formed integrally from an actuator housing.
  • the advantage of positioning the stops on the housing instead of limiting the linear adjustment of the linear drive within the linear drive is that a rotor bearing of the linear drive is arranged in a further development between the linear drive and the lever and thus the cumulative friction value, which is mainly determined by the sliding friction values within the linear drive and the stops and only negligibly by the rolling friction value of the rotor bearing, does not fluctuate as much as a combination of only sliding friction points. This means that the required drive torque of the linear drive, which is necessary to ensure secure tension in the stops, can be more precisely defined.
  • the method for securely clamping the actuator at its end points consists of a slow/decelerated approach of the linear drive to a respective stop area. This means, for example, that a spindle enclosed by the linear drive is moved to one of the stops and/or the lever to the other stop. As the process continues, the linear drive continues to move in the same direction, or a corresponding spindle continues to rotate even after the respective stop has been reached, and the linear drive, spindle or lever are moved with a defined torque, which is certainly below the maximum possible torque of a motor or electric motor that drives the linear drive or spindle. This ensures that the clamping can be safely released even when the boundary conditions change (fluctuations in lubrication, temperature and power supply, etc.) in order to be able to return to a normal operating state.
  • boundary conditions change fluctuations in lubrication, temperature and power supply, etc.
  • the first and/or second stop have a specific softness so that a predetermined linear movement of the linear drive is possible.
  • the required locking torque can also be predetermined to a reasonable value via the effective radius of the stops for the spindle or lever or their variation during design.
  • the invention relates to an actuator comprising a linear drive and gear for converting a linear movement into a rotary movement.
  • linear drives based on different principles are well known to those skilled in the art, be they mechanical or hydraulic linear drives.
  • the linear drive can be formed, for example, by a ball screw drive or a planetary roller screw drive.
  • the linear movement can accordingly be provided by a nut on a spindle or by a spindle itself.
  • the rotary movement of a shaft is generated by a lever that is connected to the shaft in a rotationally fixed manner. A rigid connection is established between the lever and the linear movement element (nut or spindle, or similar) of the linear drive by a coupling element.
  • connection point of the coupling element on the linear drive is moved linearly exclusively along a straight path
  • connection point of the coupling element on the lever is pivoted exclusively along a circular path with a predetermined radius r around the axis of the shaft, while the distance between the two connection points on the lever and on the linear drive always remains the same.
  • a trajectory of the second connection point on the lever is realized, which provides a faster angular velocity at a lower torque in a first working range and a lower angular velocity at a higher torque in a second working range to drive the shaft.
  • the shaft can produce a rotational movement with a variable
  • This rotational movement can be used to operate disconnect units, clutches, brakes or parking locks within a drive train of a motor vehicle or commercial vehicle.
  • the toggle lever mechanism described here creates a non-linear characteristic curve between the linear advance of the linear drive, e.g. a spindle path and the rotation of the lever or the drive force of the linear drive, or the spindle force and the torque of the lever.
  • This makes such an actuator particularly suitable for actuating loads that also have a non-linear actuation force characteristic curve.
  • An example of this is the actuation of a parking lock.
  • This arrangement allows the shaft for actuating the laser to be positioned very close to the linear drive - significantly closer than if a comparably large actuating torque were generated by an actuating lever alone.
  • Fig. 1 shows an actuator according to the invention with a partial sectional view
  • Fig. 2 a symbolic representation of a trajectory of the lever for shaft actuation
  • Fig. 3 an alternative arrangement of a coupling element between a lever and a spindle
  • Fig. 4 is an illustration of the torques generated by the actuator according to Fig. 3,
  • Fig. 5 and 6 an actuator according to Fig. 1 in sectional view with a lever in a first end point and a second end point
  • Fig. 7 one half of an actuator housing
  • Fig. 1 shows an actuator 1 for converting a linear movement of a linear drive 2 into a rotational movement 23,24 of a shaft 5.
  • the linear drive 2 comprises a spindle 50.
  • the spindle 50 has an end cap 51, which is connected here on one side to a coupling element 6 via a support roller 52.
  • support rollers can also be connected on both sides, each with its own coupling element.
  • the support roller 52 represents a first connection point 7 for the rotatable mounting of the coupling element 6.
  • the coupling element 6 is designed as a linearly extending, rigid sheet metal part which is connected at one end to the spindle 50 via the first connection point 7 and to a lever 4 via a second connection point 8 at the second end.
  • the coupling element 6 is also rotatably mounted on the lever 4 via the second connection point 8.
  • the lever 4 extends from its first lever end 9 with the second connection point 8 to a third connection point 10 at the second lever end 11.
  • the lever 4 is connected to a shaft 5 at the third connection point 10 in a rotationally fixed manner.
  • the lever 4 has a hole 53 with an internal toothing 54.
  • the shaft 5 has a corresponding external toothing 55 which engages in the internal toothing 54.
  • the shaft 5 is rotatably mounted in an actuator housing 40 and passes through the actuator housing 40 in the direction of a shaft axis 56.
  • the shaft axis 56 runs perpendicular both to the movement axis 41 of the spindle 50 and to the extension direction 57 of the coupling element 6.
  • the shaft 5 is connected to an actuating element 60.
  • This can be an eccentric disk, a contour disk or something similar, which is set in rotation by means of the shaft 5.
  • a parking lock, a brake, a clutch or something similar can be actuated via this actuating element 60.
  • Spindle 50, end cap 51, coupling element 6 and lever 4 are components of a gear 3, which converts a linear movement of the spindle 50 of the linear drive 2 into a rotational movement 23,24 of the shaft 5 to drive the actuating element 60.
  • the spindle 50 is in a position P1, whereby the extension direction 57 of the coupling element 6 is practically perpendicular to the movement axis 41 of the spindle 50 and to the lever 4.
  • the spindle 50 is practically fully extended and the second connection point 8 is at a second end point 22. If the spindle 50 is retracted, the corresponding travel path of the spindle 50 is coupled to a smaller travel path of the second connection point 8 perpendicular thereto via the coupling element 6.
  • the linear movement of the linear drive 2 is converted into a second rotational movement 24. In this case, a maximum torque is transmitted to the shaft 5 at a minimum rotational speed.
  • FIG. 2 An illustration of the transmitted torque and the associated rotational speed is shown in Fig. 2.
  • the second connection point 8 is located at the second end point 22, as also shown in Fig. 1, and in the right-hand part it is located at a first end point 21.
  • the first connection point 7 of the coupling element 6 is located on the movement axis 41 of the spindle 50.
  • a linear movement to retract the spindle 50 in the direction 61 pulls the lever 4 over the second connection point 8 into a second rotational movement 24 around the third connection point 10.
  • the second connection point 8 follows a trajectory 20 with the distance r between the second connection point 8 and the third connection point 10. This movement of the lever 4 is characterized by a minimum rotational speed and a maximum torque at the second end point 22.
  • the second connection point 8 is located at a first end point 21.
  • the spindle 50 is retracted so far that the lever element 4 is practically completely parallel to the spindle 50 on the movement axis 41. Moving the spindle 50 out then leads to a maximum rotational speed and minimum torque of the lever 4.
  • the lever 4 is thus driven with a non-linear torque characteristic.
  • the shaft 5 is driven accordingly and the non-linear characteristic of the shaft 5 can be used to actuate a non-linear load, such as a parking lock.
  • Fig. 3 shows an alternative arrangement of the coupling element 6 between the lever 4 and the spindle 50.
  • the spindle 50 is in the retracted position P2 here, with the second connection point 8 then being in the second end point 22'.
  • the coupling element 6 In the parallel position of the coupling element 6, it is positioned such that it covers the spindle 50 in the direction of the movement axis 41.
  • the coupling element 6 is tilted by 90°.
  • An illustration of the torques generated by this actuator can be found in Fig. 4.
  • a first end point 21' of the second connection point 8 is shown on the left side, while a second end point 22' is shown on the right side. In between, the second connection point 8 is moved along the trajectory 20'.
  • a maximum torque is transmitted to the shaft 50 at the second end point 22' (right) and a minimum torque at the first end point 21'. Accordingly, the shaft 50 is subjected to a first rotational movement 23' at the first end point 21' and a second rotational movement 24' at the second end point 22'.
  • the length of the arrows of the rotational movements 23', 24' symbolize the transmitted torque.
  • the trajectories 20 and 20' of the two alternatives in Figs. 2 and 4 are practically mirrored and do not differ in any other respects.
  • the directions of rotation are reversed at minimum and maximum torque of the shaft 5, i.e. the rotational movements 23, 23' and 24, 24' are each reversed and equal in magnitude.
  • the maximum torque is transmitted when the spindle 50 is retracted, whereas in the second alternative according to Fig. 4, it is transmitted when the spindle 50 is extended.
  • an actuator 1 according to Fig.1 shown in Fig. 3 also has a coupling element 6' with two parallel partial coupling elements 6a on both sides of the spindle 50.
  • a coupling element 6' By means of such a coupling element 6', an actuation according to the alternative in Fig. 4 is then also possible.
  • FIGs. 5 and 6 an actuator according to Fig. 1 is shown, in which the drive by a spindle drive is shown in a sectional view and further stops 30, 31 for the lever 4 and the spindle 50 are provided on the actuator housing 40.
  • the lever 4 is positioned at the first end point 21 on the first stop 30.
  • the first stop 30 is designed as an integrated component of the actuator housing 40. If a predetermined torque is now applied by the spindle 50 or by the spindle drive 70, which presses the lever 4 or the first lever end 9 against the first stop 30 with a predetermined stop force, the position of the lever 4 and thus the angular position of the shaft 5 can be clearly defined and the actuator 1 can generally be secured against adjustments, for example due to vibrations.
  • the lever 4, or the second connection point 8 is located at the second end point 22.
  • the second stop 31 is now provided for the spindle 50, or the end cap 51 of the spindle 50.
  • the spindle 50 can now be pressed against the second stop 31 with a predetermined torque.
  • the position of the lever 4 and thus the angular position of the shaft 5 can now be clearly defined and the actuator 1 can generally be secured against adjustments, for example due to vibrations.
  • Fig. 5 and 6 it is also shown that the spindle 50 is driven by a nut 71. This is connected to the spindle via a toothing point 72. Since the spindle 50 is held in the actuator housing 40 in a rotationally fixed manner, the rotational movement of the nut 71 is converted into the linear movement of the spindle 50.
  • the spindle 50 is supported on the actuator housing 40 via the nut 71 and a rotor bearing 73.
  • the drive of the nut 71 is realized via a rotor 74 of an electric motor 75.
  • the rotor bearing 73 is arranged axially between the stops 30, 31 and the rotor 74, the torque which is necessary for a secure clamping of the lever 4 or the spindle 50 at the first or second stop 30, 31 can be determined more precisely, since the cumulative friction coefficient, which is mainly determined by the sliding friction values (spindle/nut, stop surfaces) and only negligibly by the rolling friction value of the rotor bearing, does not fluctuate as much as a combination of only sliding friction points.
  • Fig. 7 one half of an actuator housing 40 is shown.
  • the actuator housing 40 has an internal contour 42. This contour 42 is embossed into the actuator housing 40 parallel to the spindle 50 and serves to accommodate a bearing element 43.
  • the bearing element 43 is, as shown in Fig. 1, arranged at one end of the spindle 50 and supports the spindle 50 on the actuator housing 40. As shown in Fig. 1, it is preferably designed as a support roller 52.
  • the bearing element 43 coincides with the first connection point 7.
  • This bearing element 43 preferably consists of two support rollers 52, which are arranged around the articulated first connection point 7 between the spindle 50 and the coupling element 6, preferably on both sides at the end of the spindle 50 and which can be supported on corresponding support surfaces 44 of the contour 42 in the actuator housing 40 and roll there.
  • the support surfaces 44 preferably run parallel to the movement axis 41 of the spindle 50 or the linearly displaceable element of the linear drive 2.
  • a non-linear actuation characteristic can be easily implemented on an actuating element 60 via a linear drive 2.
  • the stops 30, 31 provided can be used to prevent accidental adjustment due to vibrations or similar, and can also ensure a defined position of the actuator 1, e.g. in the event of a power failure. Safe actuation with good efficiency can be achieved via the support surfaces 44 in conjunction with the support rollers 52.

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

Abstract

L'invention concerne un actionneur (1) pour fournir un couple, ledit actionneur comprenant un entraînement linéaire (2) et un multiplicateur (3) pour convertir un mouvement linéaire en un mouvement de rotation, le multiplicateur (3) comprenant un levier (4) qui entraîne en rotation un arbre (5) auquel le couple doit être appliqué, le multiplicateur (3) comportant également un élément d'accouplement (6), l'élément d'accouplement (6) étant relié à l'entraînement linéaire (2) par l'intermédiaire d'un premier point de liaison (7) et au levier (4) par un second point de liaison (8) de telle sorte que l'énergie est transférée entre l'entraînement linéaire (2) et le levier (4) exclusivement par l'intermédiaire de l'élément d'accouplement (6), et l'élément d'accouplement (6) étant monté de manière rotative au niveau des deux points de liaison (7, 8).
PCT/DE2024/100163 2023-06-13 2024-02-28 Actionneur pour fournir un couple, ledit actionneur comprenant un entraînement linéaire Pending WO2024255941A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102023115292.0A DE102023115292A1 (de) 2023-06-13 2023-06-13 Aktor zur Bereitstellung eines Drehmoments mit einem Linearantrieb
DE102023115292.0 2023-06-13

Publications (1)

Publication Number Publication Date
WO2024255941A1 true WO2024255941A1 (fr) 2024-12-19

Family

ID=90364134

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2024/100163 Pending WO2024255941A1 (fr) 2023-06-13 2024-02-28 Actionneur pour fournir un couple, ledit actionneur comprenant un entraînement linéaire

Country Status (2)

Country Link
DE (1) DE102023115292A1 (fr)
WO (1) WO2024255941A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102023124630A1 (de) 2023-09-12 2025-03-13 Schaeffler Technologies AG & Co. KG Bistabiler Kniehebelaktor
DE102023124563A1 (de) 2023-09-12 2025-03-13 Schaeffler Technologies AG & Co. KG Aktor mit einem Sensorsystem zu Drehwinkelerfassung einer Welle

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015070850A1 (fr) 2013-11-18 2015-05-21 Schaeffler Technologies AG & Co. KG Support de couple d'un actionneur monté sur un carter d'embrayage/d'engrenages
DE102016207827A1 (de) 2016-05-06 2017-11-23 Schaeffler Technologies AG & Co. KG Betätigungseinheit mit einer Kurvenscheibe zum Bereitstellen einer nichtlinearen Kraft für ein Automatikgetriebe sowie Aktor mit Betätigungseinheit
DE102018116133A1 (de) 2018-07-04 2020-01-09 Schaeffler Technologies AG & Co. KG Aktor für kleine Verstellwinkel
US10669766B2 (en) * 2017-07-05 2020-06-02 Mitsuba Corporation Opening/closing body driving device
US10696379B2 (en) * 2017-03-06 2020-06-30 Lord Corporation Force sending device and a flight control device comprising such a force sensing device

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015070850A1 (fr) 2013-11-18 2015-05-21 Schaeffler Technologies AG & Co. KG Support de couple d'un actionneur monté sur un carter d'embrayage/d'engrenages
DE102016207827A1 (de) 2016-05-06 2017-11-23 Schaeffler Technologies AG & Co. KG Betätigungseinheit mit einer Kurvenscheibe zum Bereitstellen einer nichtlinearen Kraft für ein Automatikgetriebe sowie Aktor mit Betätigungseinheit
US10696379B2 (en) * 2017-03-06 2020-06-30 Lord Corporation Force sending device and a flight control device comprising such a force sensing device
US10669766B2 (en) * 2017-07-05 2020-06-02 Mitsuba Corporation Opening/closing body driving device
DE102018116133A1 (de) 2018-07-04 2020-01-09 Schaeffler Technologies AG & Co. KG Aktor für kleine Verstellwinkel

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