WO2012048694A1 - Entkoppelbarer aktuator, insbesondere mit elektromechanischem antrieb - Google Patents
Entkoppelbarer aktuator, insbesondere mit elektromechanischem antrieb Download PDFInfo
- Publication number
- WO2012048694A1 WO2012048694A1 PCT/DE2011/075210 DE2011075210W WO2012048694A1 WO 2012048694 A1 WO2012048694 A1 WO 2012048694A1 DE 2011075210 W DE2011075210 W DE 2011075210W WO 2012048694 A1 WO2012048694 A1 WO 2012048694A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- eccentric
- drive
- output
- actuator
- drive wheel
- Prior art date
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
- F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
- F16H19/08—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary motion and oscillating motion
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G21/00—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces
- B60G21/02—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected
- B60G21/04—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically
- B60G21/05—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically between wheels on the same axle but on different sides of the vehicle, i.e. the left and right wheel suspensions being interconnected
- B60G21/055—Stabiliser bars
- B60G21/0551—Mounting means therefor
- B60G21/0553—Mounting means therefor adjustable
- B60G21/0555—Mounting means therefor adjustable including an actuator inducing vehicle roll
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G21/00—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces
- B60G21/02—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected
- B60G21/04—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically
- B60G21/05—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically between wheels on the same axle but on different sides of the vehicle, i.e. the left and right wheel suspensions being interconnected
- B60G21/055—Stabiliser bars
- B60G21/0551—Mounting means therefor
- B60G21/0553—Mounting means therefor adjustable
- B60G21/0556—Mounting means therefor adjustable including a releasable coupling
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/10—Type of spring
- B60G2202/13—Torsion spring
- B60G2202/135—Stabiliser bar and/or tube
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/40—Type of actuator
- B60G2202/42—Electric actuator
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
- B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
- B60G2204/419—Gears
- B60G2204/4191—Planetary or epicyclic gears
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
- B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
- B60G2206/40—Constructional features of dampers and/or springs
- B60G2206/42—Springs
- B60G2206/427—Stabiliser bars or tubes
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2600/00—Indexing codes relating to particular elements, systems or processes used on suspension systems or suspension control systems
- B60G2600/22—Magnetic elements
-
- 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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
-
- 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
- Y10T74/00—Machine element or mechanism
- Y10T74/18—Mechanical movements
- Y10T74/18568—Reciprocating or oscillating to or from alternating rotary
Definitions
- Decoupled actuator in particular with electromechanical drive
- the invention relates to an actuator, in particular with an electromechanical drive, and is used in particular in a stabilizer for compensating vehicle movements.
- an electric drive for an adjustable stabilizer comprising a housing in which a stationary stator and coaxial thereto
- Rotor and an electronics for operating the electric drive are arranged.
- a line connection starting from the stator leads through a cover of the housing and is formed by at least one rigid bolt element.
- a rotation angle sensor assembly and an electrical connection technology which has a one-piece housing in which the electric motor for operating the at least one electromechanical stabilizer is arranged, to which an attachment component is mounted, wherein the attachment component a
- Sensor wiring harness with integrated high-current cable and a unit comprising at least one sensor for detecting the rotor position of the electric motor or a rotation angle sensor and / or a speed sensor and the electrical construction and connection technology for contacting the connecting leads of the electric motor.
- a stabilizer arrangement which comprises a stabilizer, which is operatively connected to a vehicle body and wheel guide parts, and an actuator which can be driven by means of an electric motor, through which a torsional moment counteracting a rolling moment of Stabilizer can be provided, wherein as actuator a telescoping telescopic unit is provided which comprises a telescopic cylinder for receiving at least the electric motor and a lockable in the actuator by means of a blocking piston head, via a gear translational movement of a piston head against the piston axially supported by driving the Electric motor can be introduced, resulting in a change in length of the telescopic unit.
- the telescopic unit comprises the piston head and the piston rod, wherein the piston head in the telescopic cylinder can be locked by means of a blocking device.
- a possible control of the actuator is that the piston is freely movable in the telescoping cylinder in the currentless state of the actuator.
- This freely switchable in the de-energized state actuator has a complicated structural design and a large size.
- the object of the invention is to develop an actuator, in particular with an electromechanical drive, which has a simple structural design and ensures a release for decoupling of the stabilizer halves. This object is achieved with the characterizing features of the first claim. Advantageous embodiments emerge from the subclaims.
- the actuator has in particular an electromechanical drive and a housing, wherein the drive torque provided by an electric motor is transmitted by means of a transmission between two connected to the two halves of a stabilizer outputs of the actuator and the transmission in the form of a
- the drive shaft is driven by the electric motor, with the drive shaft, a total eccentric is driven on the circumference of a drive wheel with a first outer profile and a different second outer profile is arranged, wherein in the working state of the actuator, the axis of the drive wheel through the Total eccenter eccentric to the axes of the drives is arranged and thereby each of the first
- External profiling of the drive wheel with an inner profiling of a first output and the second outer profiling are in operative connection with a second inner profiling of the second output and that this operative connection through
- the entire eccentric is connected to a drive shaft
- locking element which this in the working state, in which a torque is transmitted to the two outputs, fixed to each other so that their eccentricity added in a first position and thereby the axis of the drive wheel is eccentric to the axis of the outputs, so that the operative connection to the drives is made and that the locking element for the realization of the freewheel solves the connection between the drive eccentric and eccentric bushing, so that the drive eccentric and eccentric bushing rotate relative to each other so far that cancel in a second position whose eccentricities substantially, whereby the axis of the drive wheel substantially is placed centrally to the drives and the operative connection of the drive wheel is removed to the drives.
- the drive eccentric and the eccentric bush are also preferably fixed in position relative to one another by the locking element.
- the relative rotation between drive extender and eccentric bushing for switching from the working state (first position) to the freewheel (second position) is essentially 180 °.
- the locking element is preferably magnetically actuated. This possibility of changing the eccentric position of the drive wheel can be easily and quickly switched from the transfer mode to the freewheel. Activation of the two outputs of the actuator is particularly required for safety in case of power failure and for driving comfort increase when driving straight ahead by copying the wheel movements is avoided
- the torque-transmitting rolling elements are arranged between the outer profiles of the drive wheel and the inner profiles of the drives.
- the drive wheel of the eccentric gear in this case has a first outer profiling, which interacts with a first inner profiling of the first output via first rolling elements. Furthermore, the drive wheel is provided with a second outer profiling, which is different from the first outer profiling, said second outer profiling cooperates via second rolling elements with a second inner profiling of the second output. Due to the different pairings between the first outer profiling / first rolling elements / first inner profiling of the first output and
- the first and the second outer profile have different nominal diameters and / or different profile sizes, and the first and second rolling elements as well as the first and second internal toothing of the output drives are designed to correspond. Furthermore, the first outer profiling and the second outer profiling of the drive wheel along a longitudinal axis of the actuator are arranged one behind the other to ensure a slim design.
- the rolling elements are designed in particular in the form of rollers.
- elements in particular elastomeric rings
- the rolling elements are designed in particular in the form of rollers.
- running noises elements in particular elastomeric rings
- first and second rolling elements which transmit a radially outwardly acting biasing force to the rollers, whereby the first and second rolling elements are constantly biased against the corresponding internal profiles of the internal gears of the two outputs ,
- roller-shaped rolling elements are guided at their two ends in retaining rings, which preferably also have sound insulating properties.
- the first output of the eccentric gear which is connected to the first stabilizer half, may be formed either in the form of a rotary shaft with a fixed housing or alternatively may be formed by the housing, a first output shaft.
- the second output of the eccentric gear is designed in the form of a second output shaft, which is rotatably mounted in the housing.
- the first output shaft has a first connection element on the output side, and the second is analogous
- Output shaft provided on the output side with a second connection element which is connected to the second stabilizer half.
- Stabilizer half and / or the connection between the second output shaft and second stabilizer half provided with an overload protection in the form of a slip clutch, the respective connection when a predetermined torque is exceeded slipping and falls below this moment again attacks. This ensures that the actuator and the system are protected against overload.
- a preferred variant is the design of the connection to the
- Stabilizer halves by a longitudinal or transverse press connection, wherein in the region of the compound a layer, in particular a phosphate layer is arranged, which ensures the microforming between the respective output shaft and the stabilizer half and transmits the force occurring in the press connection force fit up to the predetermined moment. If the moment is exceeded, the
- a measuring arrangement for detecting the torsion between the first output shaft and the first stabilizer half is arranged between the first output shaft in the form of the housing and the first stabilizer half, wherein the
- Measuring arrangement is designed in particular in the form of a torque sensor whose output is coupled to a control logic that controls the engine torque as a function of the torsional moment. It is possible, a rotation of the outputs of the actuator, which has arisen due to overload, due to opposite rotation back to the desired starting position. If torsion is no longer detected by the torque sensor, the stabilizer halves will be in the required position relative to the actuator.
- an actuator of a new generation is created, which provides a large actuator torque with a smaller dimension than was previously unachievable with conventional designs
- FIG. 2 shows the section A-A according to FIG. 1,
- FIG. 3 shows the section B-B according to FIG. 1,
- FIG. 4 shows the detail X according to FIG. 1,
- FIG. 5 shows section BB through the released actuator A
- 6 shows the representation of the longitudinal section in the region of a first variant of the locking between drive eccentric and eccentric bush
- FIG. 7 shows a three-dimensional view according to FIG. 6,
- FIG. 8 shows the detail Z according to FIG. 7,
- Figure 9 shows the representation of the longitudinal section of a second variant of the lock between the drive eccentric and eccentric bushing.
- FIG. 1 a longitudinal section of an actuator A is shown, which is rotationally symmetrical and has a housing 1, in which axially behind one another
- Electric motor 2 (not shown in detail) and a transmission 3 are arranged.
- the actuator A On the side of the electric motor 2, the actuator A has a first output side
- a second output shaft 5 is provided opposite side of the output side.
- the first output shaft 4 is designed in the form of a hollow shaft stub end and provided with a bore 4.1, in which a first end 6.1 of a first half of a stabilizer (not shown) sits.
- the second output shaft 5 is also formed at its outwardly facing end in the form of a hollow shaft stub and provided with a bore 5.1, in which a second end 6.2 of the second half of the stabilizer (not shown) is arranged.
- the ends 6.1, 6.2 are in the holes 4.1, 5.1 by means of a
- Holes 4.1, 5.1 are provided with a coating in particular a phosphate layer, which ensures the microforming between the respective output shaft 4, 5 and the ends 6.1, 6.2 of the stabilizer halves and transmits the frictional connection acting through the press connection only up to the predetermined moment, so that a Overload protection is formed, which solves the respective connection at a predetermined torque is exceeded and closes when falling below this moment. This ensures safety in the event of overload.
- the shaft 2.1 of the electric motor 2 is connected to the drive shaft 3.1 of the transmission 3, which is designed as an eccentric gear.
- a drive eccentric 3.2 is arranged, which is formed here in one piece with the drive shaft 3.1.
- On the drive eccentric 3.2 sits an eccentric bushing 3.3 by means of which a drive wheel 3.4, can be driven.
- a first outer profiling 8 of the drive wheel 3.4 corresponds via first rolling elements 9 with an inner profiling 10 of the first output 11, which is formed on the inside of the housing 1, whereby a rotational movement can be transmitted to the first drive shaft 4 via the housing 1 (see also FIG ).
- the second outer profiling 8 of the drive wheel 3.4 formed differently (smaller diameter, less profile elements) and axially offset the second outer profile 12 of the drive wheel 3.4 is provided, the second
- External profiling 12 via second rolling elements 13 with a second inner profiling 14 of the second output 15 corresponds (see also Figure 3).
- the second output 15 is fixedly connected to the second output shaft 5, so that a rotational movement to the second output shaft 5 is transferable.
- the rolling elements 9, 13 are designed in the form of rollers and are accommodated at the ends in retaining rings 17 (see FIG. 4) which assume an axial fixation.
- the first and second outer profiles 8, 12 of the drive wheel 3.4 and the first and second inner profiles 10, 14 are adapted to the diameter of the rolling elements 9, 13 and formed substantially by longitudinally extending circular segment-shaped wells.
- a further advantageous embodiment of the actuator is that the connection between the first outer profiling 8 and the second outer profiling 12 of the drive wheel 3.4 on the one hand and the first and the second inner profiling 10, 14 of the first and second output 1 1, 15 on the other hand in a second position is separable, such that both outputs 1 1, 15 and thus both output shafts 4, 5 are freely rotatable relative to each other by the positive connection between the drive wheel 3.4 and the first and second rolling elements 9, 13 is released, so that practically a "release" of the actuator A is guaranteed.
- the first output shaft 4 and the second output shaft 5 can rotate freely against each other.
- the actuator is de-energized (FailSafe state).
- Eccentric bushing 3.3 bearing drive 3.4 again moved eccentrically so that its outer profiles 10, 14 again engage with the rolling elements and a torque on the outputs 1 1, 15 is transmitted, creating a
- On-board electronics / engine electronics of the vehicle is in communication.
- the relative rotation between drive eccentric 3.2 and eccentric bushing 3.3 can be done by an actuation and locking mechanism with which they are separable and locked in the required, offset at an angle of 180 ° positions (in the first position and the second position) again.
- the unlocking has an axially actuable bolt in the form of a locking bolt 21, which is arranged by means of a fastening element 21 .1 on the drive eccentric 3.2 and against the spring force of a return spring 22 by means of a
- Magnets 23 is axially actuated by a sliding sleeve 23.1.
- the locking pin 21 has in the direction of the end face 3.3 'of the eccentric bushing 3.3 a first
- Locking pin 24 and a second locking pin 25 arranged and axially biased by means of a respective compression spring 26.
- the locking pins 24, 25 are radially fixed in position on the stops 21.3 and 21 .4 of the locking pin 21, so that drive eccentric 3.2 and eccentric bushing 3.3 are in a fixed position in which the Added eccentricity. If a release is to be realized by the
- Locking position which is determined by the stops 21.3 and 21.4 and it is again a torque to the drives or drive shafts transferable.
- Eccentric bushing 3.3 realized by an actuating and locking mechanism which is formed in the manner of a rocker 30.
- This rocker 30 is rotatably connected to the drive eccentric 3.2 and has two axially actuated bolts in the form of a first locking bolt 31 .1, and a second locking bolt 31.2, the offset at an angle of 180 ° to each other and so pivotally mounted on the drive shaft or Drive eccentric are mounted, that during an axial forward movement of the first locking bolt 31 .1 of the second
- Locking bolt 31.2 performs an axial backward movement by the same amount and vice versa.
- the axial actuation also takes place via a magnet, which is not shown in FIG.
- Drive eccentric 3.2 has in the direction of the rocker 30 a driver 32 with axial offset by 180 ° to each other guide holes 33 in which the first and second locking pin 31 .1, 31.2 are guided axially.
- the eccentric bushing 3.3 has a balance weight 34 into which the first or the second bolt engage. The balance weight 34 rotates to change the operating condition 180 ° and locked either with the first locking pin 31.1 in the first position, in which the eccentricities of drive eccentric 3.2 and
- a corresponding measuring arrangement for measuring the torsion, which is coupled to a control logic that regulates the engine torque as a function of the torsional moment. For this purpose, e.g. between the first
- Stabilizer half arranged a measuring arrangement for detecting the torsion between the first output shaft 4 and the first stabilizer half 6.1 (not shown), wherein the measuring arrangement is in particular in the form of a torque sensor whose output is coupled to the control logic.
- This measuring arrangement can be arranged for example in a tubular shape of the housing or on the front side of the housing.
- a measuring arrangement for detecting the torsion which works on the basis of the inverse magnetostriction.
- a region of the stabilizer which is subjected to torsion e.g., the first
- Stabilizer 6a provided with a magnetization or magnetized.
- the area is surrounded by a bush in which a coil arrangement is integrated. If the corresponding area of the stabilizer is subjected to torsion, then it changes due to these mechanical stresses in the magnetized area the
- Magnetization This is detected by the coil arrangement and evaluated as a measure of the torsional stress. It is of great advantage here that the forces acting on the shaft (for example the stabilizer part 6a) have an almost linear effect on the magnetic field, whereby the measurement of the torsion can be realized with a very high accuracy.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/820,889 US8864154B2 (en) | 2010-09-06 | 2011-09-05 | Actuator that can be decoupled, in particular having an electromechanical drive |
DE112011102960T DE112011102960A5 (de) | 2010-09-06 | 2011-09-05 | Entkoppelbarer Aktuator, insbesondere mit elektromechanischem Antrieb |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE202010008467U DE202010008467U1 (de) | 2010-09-06 | 2010-09-06 | Entkoppelbarer Aktuator, insbesondere mit elektromechanischem Antrieb |
DE202010008467.9 | 2010-09-06 |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2012048694A1 true WO2012048694A1 (de) | 2012-04-19 |
WO2012048694A4 WO2012048694A4 (de) | 2012-05-31 |
Family
ID=45443783
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2011/075210 WO2012048694A1 (de) | 2010-09-06 | 2011-09-05 | Entkoppelbarer aktuator, insbesondere mit elektromechanischem antrieb |
Country Status (3)
Country | Link |
---|---|
US (1) | US8864154B2 (de) |
DE (3) | DE202010008467U1 (de) |
WO (1) | WO2012048694A1 (de) |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013002713B4 (de) | 2013-02-16 | 2014-08-28 | Audi Ag | Drehstabfederanordnung für eine Radaufhängung eines Kraftfahrzeugs |
KR101504253B1 (ko) * | 2013-11-29 | 2015-03-19 | 현대모비스 주식회사 | 차량용 액추에이터 |
DE102014205261A1 (de) * | 2014-03-20 | 2015-09-24 | Zf Friedrichshafen Ag | Schwenkmotor eines aktiven Wankstabilisators für Kraftfahrzeuge |
JP2016034800A (ja) * | 2014-08-04 | 2016-03-17 | Ntn株式会社 | スタビライザー装置 |
DE102014221129A1 (de) * | 2014-10-17 | 2016-04-21 | Schaeffler Technologies AG & Co. KG | Wankstabilisator für ein Kraftfahrzeug |
WO2017042055A1 (de) * | 2015-09-07 | 2017-03-16 | Bayerische Motoren Werke Aktiengesellschaft | Dämpfungssystem eines zweispurigen fahrzeugs |
DE102015217045A1 (de) | 2015-09-07 | 2017-03-09 | Volkswagen Aktiengesellschaft | Nutzfahrzeuglenkung |
US10618370B2 (en) * | 2016-09-02 | 2020-04-14 | Mando Corporation | Active roll stabilizer |
WO2020018900A1 (en) * | 2018-07-20 | 2020-01-23 | American Axle & Manufacturing, Inc. | Disconnecting stabilizer bar assembly having disconnect mechanism with reduced backlash |
DE102019119658A1 (de) * | 2019-07-19 | 2021-01-21 | Pilz Gmbh & Co. Kg | Zykloidgetriebe mit Drehmomenterfassungseinrichtung |
US11565567B2 (en) * | 2021-05-25 | 2023-01-31 | Ford Global Technologies, Llc | Invertible stabilizer bar and system incorporating the same |
US11993127B2 (en) * | 2022-01-20 | 2024-05-28 | Schaeffler Technologies AG & Co. KG | Roll stabilizer assembly |
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JPS60234171A (ja) | 1984-05-08 | 1985-11-20 | Omron Tateisi Electronics Co | 歯車機構のバツクラツシユ調整装置 |
DE19714565A1 (de) | 1996-06-28 | 1998-01-08 | Mannesmann Sachs Ag | Stablisatoranordnung |
WO2001051301A1 (de) * | 2000-01-13 | 2001-07-19 | Bayerische Motoren Werke Aktiengesellschaft | Elektromechanischer stabilisator für das fahrwerk eines fahrzeuges |
EP1821390A2 (de) | 2006-02-21 | 2007-08-22 | Zf Friedrichshafen Ag | Elektrischer Antrieb für einen verstellbaren Stabilisator |
US20080150241A1 (en) * | 2006-12-22 | 2008-06-26 | Honda Motor Co., Ltd. | Reduction gear and vehicular active stabilizer system |
DE102008018610A1 (de) * | 2007-04-13 | 2008-10-16 | Asturia Automotive Systems Ag | Stabilisatoranordnung |
EP2068037A1 (de) * | 2006-09-25 | 2009-06-10 | Nabtesco Corporation | Exzentrisch oszillierendes untersetzungsgetriebe und das exzentrisch oszillierende untersetzungsgetriebe verwendende stabilisatorwellendrehvorrichtung |
DE102008000148A1 (de) | 2008-01-25 | 2009-07-30 | Zf Friedrichshafen Ag | System umfassend zumindest einen Stabilisator, eine Drehzahl- und/oder Drehwinkelsensoranordnung und eine Verbindungstechnik |
DE202008013633U1 (de) * | 2008-10-19 | 2010-03-18 | Asturia Automotive Systems Ag | Differential-Exzentergetriebe |
JP2010234947A (ja) * | 2009-03-31 | 2010-10-21 | Aisin Seiki Co Ltd | スタビライザ制御装置 |
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US6126566A (en) * | 1997-11-03 | 2000-10-03 | Ker-Train Holdings Ltd. | Coplanar reverted gear train loop |
US6149166A (en) * | 1998-07-24 | 2000-11-21 | Trw Inc. | Apparatus for use in a vehicle suspension |
DE19937412A1 (de) * | 1999-08-07 | 2001-02-15 | Rudolf Braren | Zykloidengetriebe |
DE102004048085A1 (de) * | 2004-09-30 | 2006-04-06 | Zf Friedrichshafen Ag | Schaltbarer Stabilisator für ein Kraftfahrzeug |
DE102006040109A1 (de) * | 2006-08-26 | 2008-02-28 | Bayerische Motoren Werke Ag | Aktiver, geteilter Kraftfahrzeugstabilisator mit eingebauten Schwenkmotor |
US7832739B2 (en) * | 2006-11-06 | 2010-11-16 | American Axle & Manufacturing, Inc. | Apparatus and method for coupling a disconnectable stabilizer bar |
DE102007032318A1 (de) * | 2007-07-11 | 2009-01-15 | Bayerische Motoren Werke Aktiengesellschaft | Elektrischer Aktuator für einen geteilten Kraftfahrzeugstabilisator |
DE202008012581U1 (de) * | 2008-09-22 | 2010-02-18 | Asturia Automotive Systems Ag | Stabilisatoranordnung |
-
2010
- 2010-09-06 DE DE202010008467U patent/DE202010008467U1/de not_active Expired - Lifetime
-
2011
- 2011-09-05 DE DE102011053278A patent/DE102011053278A1/de not_active Withdrawn
- 2011-09-05 WO PCT/DE2011/075210 patent/WO2012048694A1/de active Application Filing
- 2011-09-05 DE DE112011102960T patent/DE112011102960A5/de not_active Ceased
- 2011-09-05 US US13/820,889 patent/US8864154B2/en not_active Expired - Fee Related
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EP1821390A2 (de) | 2006-02-21 | 2007-08-22 | Zf Friedrichshafen Ag | Elektrischer Antrieb für einen verstellbaren Stabilisator |
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US20080150241A1 (en) * | 2006-12-22 | 2008-06-26 | Honda Motor Co., Ltd. | Reduction gear and vehicular active stabilizer system |
DE102008018610A1 (de) * | 2007-04-13 | 2008-10-16 | Asturia Automotive Systems Ag | Stabilisatoranordnung |
DE102008000148A1 (de) | 2008-01-25 | 2009-07-30 | Zf Friedrichshafen Ag | System umfassend zumindest einen Stabilisator, eine Drehzahl- und/oder Drehwinkelsensoranordnung und eine Verbindungstechnik |
DE202008013633U1 (de) * | 2008-10-19 | 2010-03-18 | Asturia Automotive Systems Ag | Differential-Exzentergetriebe |
JP2010234947A (ja) * | 2009-03-31 | 2010-10-21 | Aisin Seiki Co Ltd | スタビライザ制御装置 |
Also Published As
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DE202010008467U1 (de) | 2011-12-07 |
US8864154B2 (en) | 2014-10-21 |
WO2012048694A4 (de) | 2012-05-31 |
DE102011053278A1 (de) | 2012-03-08 |
US20130291664A1 (en) | 2013-11-07 |
DE112011102960A5 (de) | 2013-06-06 |
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