WO2016055359A1 - Mécanisme de commande linéaire et ensemble moteur-générateur - Google Patents

Mécanisme de commande linéaire et ensemble moteur-générateur Download PDF

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Publication number
WO2016055359A1
WO2016055359A1 PCT/EP2015/072752 EP2015072752W WO2016055359A1 WO 2016055359 A1 WO2016055359 A1 WO 2016055359A1 EP 2015072752 W EP2015072752 W EP 2015072752W WO 2016055359 A1 WO2016055359 A1 WO 2016055359A1
Authority
WO
WIPO (PCT)
Prior art keywords
guide
linear actuator
ring
adjusting
adjusting ring
Prior art date
Application number
PCT/EP2015/072752
Other languages
German (de)
English (en)
Inventor
Dirk Zeise
Andreas Lenz
Georg-Friedrich LÜHRS
Original Assignee
Volkswagen Aktiengesellschaft
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 Volkswagen Aktiengesellschaft filed Critical Volkswagen Aktiengesellschaft
Publication of WO2016055359A1 publication Critical patent/WO2016055359A1/fr

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Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/06—Means for converting reciprocating motion into rotary motion or vice versa
    • 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
    • F16H25/186—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions with reciprocation along the axis of oscillation

Definitions

  • the invention relates to a linear actuator comprising
  • a setting wheel which is designed as a ring gear rotatably mounted in a housing
  • a positioning drive coupled to the setting wheel for rotational adjustment of the ring gear in defined angular positions
  • guide structures which comprise a plurality of guide bodies and by means of which a rotational movement of the setting wheel in an axial displacement of
  • Adjusting ring is changeable.
  • the invention further relates to a motor-generator arrangement comprising
  • linear actuators and motor-generator arrangements are known from the post-published German patent application DE 10 2013 006168.7.
  • a linear actuator is described, which is adapted to be coaxially mounted on the rotor shaft of an electric machine to switch there provided, a switchable planetary gear, in particular selectively either the sun gear or its web rotatably coupled to the rotor shaft.
  • a switchable planetary gear in particular selectively either the sun gear or its web rotatably coupled to the rotor shaft.
  • Linear actuator has a statorfestes housing in which a both externally and internally toothed, here addressed as a thumbwheel ring gear is rotatably mounted.
  • the external toothing of the setting wheel meshes with a likewise mounted in the housing drive pinion, which is provided with a servomotor.
  • the setting wheel is motor-rotatable by defined angle.
  • a collar Concentrically within the setting wheel, a collar is arranged, which is mounted via a ball bearing radially inward against a sliding sleeve. Adjusting ring and sliding sleeve are rotatably coupled via the ball bearing against each other, but axially fixed to each other.
  • Adjusting ring is at least three defined locations with an axially aligned
  • Gearing sections of the adjusting ring are thus perpendicular to the aligned in the circumferential direction of the internal toothing of the adjusting wheel.
  • so-called hedgehog wheels are positioned, which are provided on their surface with a plurality of individual teeth, wherein the teeth in their entirety spirally with a plurality of turns around the hedgehog wheel rotation axis and groups in axially aligned and evenly over the hedgehog Circumferentially distributed rows are arranged on the hedgehog wheel surface.
  • This hedgehog gearing is thus able to both with the
  • Patent application specified a generic motor-generator arrangement.
  • a disadvantage of the known linear actuator is in particular the complex production of the hedgehog wheels.
  • the practice has shown that in particular the meshing between the hedgehog wheels and the toothed portions of the adjusting ring tends to tension, which can be solved only with a high release torque, which has to apply the drive pinion. It is the object of the present invention to propose a generic linear actuator and according to a generic motor-generator arrangement with simplified production and improved reliability.
  • the guide structures further comprise a plurality of uniform, azimuthal, i. in the circumferential direction, staggered guide grooves, which are introduced into a first of the guide surfaces and these rotate spirally and in each of which one of the distributed over the circumference of the other of the guide surfaces, in each case in the radial direction a circular cross-section having guide body is guided.
  • a switching unit for a planetary gear on an electric motor drive of a motor vehicle high forces, but also tend to be purely thread-based, actuators for clamping, especially if the thread pitch is chosen so small that they are to hold the inlaid gears required self-locking shows.
  • the invention therefore goes on and allows instead of the thread on the one hand guide grooves and on the other hand in cross-section round guide body interact with each other.
  • the azimuthal, ie offset in the circumferential direction guide grooves are basically comparable to the gears a multi-thread. Unlike the multi-course However, threads do not engage in these guide grooves, no spiral ribs, but said guide body according to the invention with a round cross-section.
  • the guide bodies are arranged distributed over the circumference of the guide not containing guide surface, so that acting on the adjusting ring tilting moment is supported.
  • the azimuthal offset of the guide body to one another corresponds to the azimuthal offset of the guide grooves to each other, it is possible to arrange the guide body in a common, perpendicular to the axial direction guide plane.
  • a stable against tilting, yet voltage-proof linear actuator can be provided. Due to the circular cross-section of the guide body, whose diameter preferably corresponds to the clear width of the correspondingly shaped guide grooves, a secure and nevertheless low-friction guidance is achieved.
  • the spiral pitch of the guide grooves may be different in sections.
  • "kinks" in the course of the guide grooves are possible, of course, all grooves have to show at the corresponding point the same "kink”. Due to the round cross section of the guide body, a smooth transition from one pitch section to the next is possible.
  • the spiral pitch of the guide grooves is different in sections, wherein one or more sections have a spiral pitch of zero. This makes a faster approach to selected axial positions possible. Those skilled in the art will recognize that when the guide bodies are in ranges of spiral pitch from zero to the associated one
  • Axial positions of the adjusting ring correspond to certain switching positions coupled to the linear actuator gear, the sections
  • park sections Between the park sections are sections of non-vanishing spiral pitch of the guide grooves, here as Transition sections are to be designated. Rotates the thumbwheel while the
  • Transfer area are led to another parking area to drive the wheel at high speed, with a deceleration must be initiated only after reaching the desired axial position of the adjusting ring.
  • the extent of the parking area can be used to decelerate, without that during the deceleration still taking place residual rotation of the adjusting wheel would lead to a further axial displacement of the adjusting ring. In other words, the entire transfer area with
  • Maximum speed i. the actual axial adjustment can be done at maximum speed, resulting in reduced switching times.
  • the guide bodies are formed as radially extending guide pins, which are each held in a holder in the guide not having guide surface. These pins can be firmly connected to their brackets. Due to its round cross-section, the friction-inducing contact of the guide pins with the walls of the guide groove into which they engage is radial to two, i. limited pin-axially aligned contact lines.
  • the guide pins may be rotatably mounted in their brackets around their respective radial pin axis. This is particularly favorable in cases of guide grooves with alternating spiral pitch when driving around the curves or kinks.
  • the guide body are formed as a guided in an annular groove in the guide grooves not having guide surface guided balls.
  • the spherical shape has the advantage of being rotatable about all axes, not, as with the guide pins, only about radially aligned axes.
  • the contact surface on the walls of the guide grooves is further reduced.
  • the adjusting ring is secured against rotation on the housing fixed, recesses of the adjusting ring axially sweeping torque supports.
  • Guide bodies which are fixed to the collar is a rotation lock mandatory.
  • a rotation assurance appears at least advantageous.
  • torque supports can be fixed together on a torque support ring, which in turn is rotatably connected to the housing.
  • an outer bearing is considered to be favorable for the storage of the adjusting wheel, in which the adjusting wheel is mounted on the drive pinion and a plurality of azimuthally offset from the drive pinion, meshing with the external toothing of the adjusting wheel guide pinions.
  • the outer toothing can be fully formed or composed of spaced outer toothed segments.
  • the thumbwheel is mounted axially on both sides.
  • the linear actuator according to the invention is basically suitable for any application in which a precise axial adjustment of any component is required. However, it is particularly preferably used as a gear plate for switching a switchable planetary gear set on the rotor shaft of an engine-generator arrangement of a motor vehicle drive train.
  • Figure 1 is an exploded view of a first embodiment
  • Figure 2 is a sectional view through the linear actuator of Figure 1 in
  • Figure 3 is a perspective view of the linear actuator of Figure 1 in
  • Figure 4 is a perspective view of the adjusting wheel of the linear actuator of
  • FIG. 1 A first figure.
  • FIG. 5 is a sectional view of the setting wheel of FIG. 4;
  • FIG. 6 shows a schematic representation of the groove guide in the setting wheel of FIG. 4,
  • Figure 7 is an exploded view of adjusting ring, sliding sleeve and more
  • FIG. 8 three sectional views of the linear actuator of FIG. 1 in the assembled state to illustrate the three switching positions;
  • FIG. 10 a sectional view of the linear actuator of FIG. 9 in FIG.
  • Figure 1 1 a perspective view of the linear actuator of Figure 9 in
  • FIG. 12 is a perspective view of the setting wheel of the linear actuator of FIG. 12
  • FIG. 13 is a sectional view of the setting wheel of FIG. 12;
  • Figure 14 an exploded view of adjusting wheel, adjusting ring, sliding sleeve and more
  • FIG. 15 a perspective view of the components of FIG. 14 in FIG.
  • FIG. 16 an exploded view of a further embodiment of a setting wheel.
  • FIGS. 1-8 show a first embodiment of the invention
  • Linear actuator 10 in different representations to illustrate different aspects.
  • the following description refers primarily to the complete illustration in Figure 1, wherein the expert finds by comparing the reference numerals the corresponding elements in the detail views of Figures 2 to 7 easily. These should be addressed only selectively. To explain the different
  • FIGS. 9-15 illustrate a second embodiment of the invention
  • Linear actuator 10 ' show, but here was waived an explicit representation of the different switching positions.
  • the primed reference symbols ( ⁇ ') used in FIGS. 9-15 correspond to the functionally equivalent elements with numerically identical reference symbols in FIGS. 1-8.
  • the linear actuator 10 of Figure 1 as can be seen particularly in Figure 3, constructed as an independent module, which is bounded by the two-part housing, consisting of the housing shells 12a and 12b to the outside.
  • This housing is in the preferred application, in which the linear actuator 10 is used to switch a arranged on the rotor shaft of an electric machine planetary gear, arranged statorfest.
  • the thumbwheel 14 is rotatably mounted. It has one
  • Embodiment also its storage in the housing 12a, b is used. So combs the
  • FIGS. 4-6 show a schematic development of the inner circumferential surface 142 of the setting wheel 14.
  • FIG. 6 shows a schematic development of the inner circumferential surface 142 of the setting wheel 14.
  • the Inner peripheral surface 142 basically spirally encircling guide grooves 143 each have three sections disappearing spiral slope and two sections connecting these sections constant spiral slope on.
  • the sections of disappearing spiral pitch are to be referred to below as parking sections 144, while the sections of constant spiral pitch between them are to be addressed as transition sections 145. Their importance will be discussed further below.
  • a collar 16 is arranged.
  • a detailed representation of the adjusting ring 16 can be found in Figure 7.
  • the adjusting ring 16 is characterized in particular by three round in profile guide pins 161, which are in corresponding holders, formed as radial holes 162 in the outer peripheral surface 163 of the adjusting ring 16, fixed. In the illustrated embodiment, they are pressed so that they are completely fixed, but it is also conceivable for a rotatable about the respective radial axis storage.
  • Guide pins 161 are uniform, i. in the embodiment shown by an angle of 120 °, distributed over the circumference of the adjusting ring 16. In the assembled state they engage, as can be seen in particular in Figure 2, in the guide grooves 143 of the adjusting wheel 14 a. Each guide pin 161 engages as the only one in each of its associated guide groove 143 a. With the same azimuthal offset of the guide pins 161 and the guide grooves 143, as in the embodiment shown, the
  • Guide pins 161 may be arranged in the same, oriented perpendicular to the axis of the linear actuator 10 level. The person skilled in the art will recognize that a relative rotation of the setting wheel 14 to the adjusting ring 16 leads to a relative axial displacement of the adjusting ring 16 and the adjusting wheel 14 - in any case, when the guide pins 161 straight in
  • Transition portions 145 of the guide grooves 143 engage. In contrast, a relative rotation of setting wheel 14 and collar 16 then does not lead to a relative
  • the adjusting ring 16 is characterized in the embodiment shown by axialnutmé recesses 164 in its outer peripheral surface 163. These serve the
  • the rotation lock is realized by angular-like moment supports 18 which are fixed to the housing shell 12b, the entire housing 12a, b and in particular the recesses 164 of the adjusting ring 16 pass through and are connected to the housing shell 12a fixed counterparts 20. Consequently, a rotation of the adjusting wheel 14 according to the mechanism explained above always lead to a step-like axial displacement of the rotationally secured adjusting ring 16.
  • a ball bearing 22 is pressed. It is used for the rotational decoupling of the adjusting ring 16 by a sliding sleeve 24, which is arranged radially within the adjusting ring 16.
  • the sliding sleeve has an internal spline 241, with which it is rotatably but axially displaceable on the rotor shaft of an electric machine, not shown fixed.
  • Axial is the sliding sleeve 43 in the assembled state on the housing shell 12b and carries in this area an external toothing 242, the optional rotational fixation of
  • FIG. 1 Further illustrated in Figure 1 are a support ring 26 and a fixing ring 28, whose functions will be readily apparent to those skilled in the art, but which are not important for the basic structure of the linear actuator according to the invention.
  • Linear actuator 10 ' as shown in Figures 9-15, can basically be referred to the above. In the following, only the essential
  • a first essential difference is the design of the guide bodies, i. those elements which engage in the guide grooves 143 'of the setting wheel 14'.
  • these are formed as guide balls 161 '.
  • the corresponding holder in the adjusting ring 16 ' is therefore as a the outer circumference of the
  • Adjusting ring 16 'circumferential groove 162' is formed. To a rotation of the
  • the torque supports 18' are modified compared to the first embodiment and in particular have axial slots 181 ', in which the guide balls 161' lie. Axially, the guide balls 161 'are therefore fixed by the groove 164' of the adjusting ring 16 '; they are azimuthally secured by the slots 181 'of the moment supports 18'.
  • a special anti-rotation of the adjusting ring 16 ' is shown in the
  • the torque supports 18 ' can be modified so that they secure both the guide balls 161' and the adjusting ring 16 'itself.
  • Another special feature of the second embodiment of the invention is the storage of the setting wheel 14 '. This is done here by an inner ball bearing.
  • the setting wheel 14 ' This is done here by an inner ball bearing.
  • Setting wheel 14 radially between its outer circumference and its inner circumference a guide surface 146' projecting on both sides of its wheel surface, run on the corresponding bearing balls 147 '.
  • the bearing balls 147 ' are counter-mounted in corresponding, housing-fixed support rings 26'.
  • FIG. 16 shows a further embodiment of a setting wheel 14 ", which is to be discussed on the basis of its distinction to the very similarly constructed setting wheel 14 of Figures 4 to 6.
  • Figure 16 shows the single-line parts of the setting wheel 14" for better visibility, which in the final assembled state is a common one Make up welding group, in
  • a carrier ring 147 "forms the basic structure of the setting wheel 14".
  • Transition portions 145 " the same linear displacement of a collar, not shown in Figure 16 can be achieved with a smaller angle of rotation.

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

Abstract

L'invention concerne un mécanisme de commande linéaire, comprenant : - une roue de positionnement (14, 14'), se présentant sous la forme d'une couronne montée rotative dans un carter, - un mécanisme de commande accouplé à la roue de positionnement (14, 14') servant au réglage par rotation de la couronne dans des positions angulaires définies, - une bague de positionnement (16, 16') disposée coaxialement à l'intérieur de la roue de positionnement (14, 14') et pouvant se déplacer axialement par rotation de la roue de positionnement (14, 14'), et - un manchon coulissant (24, 24') disposé coaxialement à l'intérieur de la bague de positionnement (16, 16') et raccordé, de manière fixe axialement et découplée en rotation, à la bague de positionnement (16, 16'). La surface périphérique intérieure (142, 142') de la roue de positionnement et la surface périphérique extérieure (163, 163') de la bague de positionnement (16, 16') forment deux surfaces de guidage interagissantes qui présentent des structures de guidage mécaniques comprenant une pluralité de corps de guidage (161, 161'), au moyen desquelles un mouvement de rotation de la roue de positionnement (14, 14') peut être converti en un coulissement axial de la bague de positionnement (16, 16'). L'invention est caractérisée en ce que les structures de guidage présentent en outre une pluralité de rainures de guidage (143, 143') uniformes, décalées les unes par rapport aux autres de manière azimutale, qui sont ménagées dans une première des surfaces de guidage (142, 142') et parcourent celle-ci en forme de spirale et dans lesquelles est guidé respectivement un des corps de guidage (161, 161') répartis sur la périphérie des autres surfaces de guidage (163, 163'), présentant chacun une section transversale ronde dans le sens radial.
PCT/EP2015/072752 2014-10-08 2015-10-01 Mécanisme de commande linéaire et ensemble moteur-générateur WO2016055359A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014220396 2014-10-08
DE102014220396.1 2014-10-08

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Publication Number Publication Date
WO2016055359A1 true WO2016055359A1 (fr) 2016-04-14

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WO (1) WO2016055359A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111971494A (zh) * 2018-04-13 2020-11-20 克诺尔商用车制动系统有限公司 换挡致动器
WO2022176579A1 (fr) * 2021-02-18 2022-08-25 ユニプレス株式会社 Transmission en deux étapes pour automobile électrique

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4041873A1 (de) * 1990-05-29 1991-12-05 Asahi Optical Co Ltd Fuehrungseinrichtung mit einem kurvenring
DE102009024328A1 (de) * 2008-07-21 2010-01-28 Schaeffler Kg Verstelleinheit
DE102009013121A1 (de) * 2009-03-13 2010-09-16 Schaeffler Technologies Gmbh & Co. Kg Geregelte axiale Vorspanneinheit
DE102012202456A1 (de) * 2012-02-17 2013-08-22 Schaeffler Technologies AG & Co. KG Axialverstelleinheit
DE102013002382A1 (de) * 2013-02-11 2014-08-28 Alfred Brühn Pneumatische Schaltbetätigung für automatische und automatisierte Fahrzeuggetriebe

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013006168A1 (de) 2013-04-10 2014-10-16 Volkswagen Aktiengesellschaft Linearstellantrieb und Motor-Getriebeanordnung mit einem solchen

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4041873A1 (de) * 1990-05-29 1991-12-05 Asahi Optical Co Ltd Fuehrungseinrichtung mit einem kurvenring
DE102009024328A1 (de) * 2008-07-21 2010-01-28 Schaeffler Kg Verstelleinheit
DE102009013121A1 (de) * 2009-03-13 2010-09-16 Schaeffler Technologies Gmbh & Co. Kg Geregelte axiale Vorspanneinheit
DE102012202456A1 (de) * 2012-02-17 2013-08-22 Schaeffler Technologies AG & Co. KG Axialverstelleinheit
DE102013002382A1 (de) * 2013-02-11 2014-08-28 Alfred Brühn Pneumatische Schaltbetätigung für automatische und automatisierte Fahrzeuggetriebe

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111971494A (zh) * 2018-04-13 2020-11-20 克诺尔商用车制动系统有限公司 换挡致动器
JP7050950B2 (ja) 2018-04-13 2022-04-08 クノル－ブレムゼ ジステーメ フューア ヌッツファールツォイゲ ゲゼルシャフト ミット ベシュレンクテル ハフツング ギアシフトアクチュエータ
US11378183B2 (en) 2018-04-13 2022-07-05 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Gearshift actuator
WO2022176579A1 (fr) * 2021-02-18 2022-08-25 ユニプレス株式会社 Transmission en deux étapes pour automobile électrique
US11933398B2 (en) 2021-02-18 2024-03-19 Unipres Corporation Two-speed transmission apparatus for electric vehicle

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