EP2021646A1 - Einrichtung zur axialeinstellung wenigstens eines lamellenschaltelementes - Google Patents
Einrichtung zur axialeinstellung wenigstens eines lamellenschaltelementesInfo
- Publication number
- EP2021646A1 EP2021646A1 EP07729512A EP07729512A EP2021646A1 EP 2021646 A1 EP2021646 A1 EP 2021646A1 EP 07729512 A EP07729512 A EP 07729512A EP 07729512 A EP07729512 A EP 07729512A EP 2021646 A1 EP2021646 A1 EP 2021646A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- switching element
- grooves
- ball ramp
- wheel
- axial adjustment
- 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.)
- Withdrawn
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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
- F16H48/34—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D28/00—Electrically-actuated clutches
-
- 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
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
-
- 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
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
- F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet gears
-
- 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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/22—Arrangements for suppressing or influencing the differential action, e.g. locking devices using friction clutches or brakes
-
- 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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/295—Arrangements for suppressing or influencing the differential action, e.g. locking devices using multiple means for force boosting
-
- 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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
-
- 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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H2048/204—Control of arrangements for suppressing differential actions
-
- 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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
- F16H48/34—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators
- F16H2048/343—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators using a rotary motor
-
- 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
- F16H48/00—Differential gearings
- F16H48/38—Constructional details
- F16H48/42—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon
- F16H2048/423—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon characterised by bearing arrangement
-
- 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
- F16H48/00—Differential gearings
- F16H48/38—Constructional details
- F16H48/40—Constructional details characterised by features of the rotating cases
Definitions
- the invention relates to a device for axial adjustment of at least one lamellar switching element according to the closer defined in the preamble of claim 1 species,
- Such a device for the axial adjustment of a lamellar switching element is known, for example, from EP 0 340 451 A2.
- a device for axial adjustment is described which actuates a friction arrangement via a pressure ring by means of a selectively actuatable rotary drive.
- an adjusting ring which can be driven by an electric motor via a pinion is provided. which causes an axial displacement of the pressure ring.
- the pressure ring is itself arranged non-rotatably with respect to a housing.
- control curves or control profiles are provided, which have a non-linear rate of change of the thrust ring effective axial component over the angle of rotation of the adjusting ring, and which between the pressure ring and the adjusting ring in ab leveragender, the pressure ring at rotation the adjusting ring shifting operative connection stand. It is u. a. proposed to perform the cams as located in the adjusting ring and the pressure ring grooves, wherein the adjusting ring interacts with the pressure ring by means of balls, which are located in the mutually corresponding grooves of the adjusting ring and the pressure ring.
- the control cam has a non-linear rate of change, whereby in a first phase of the operation of the friction arrangement, a steep increase of the effective axial components to overcome the play of fins of the friction arrangement a strong spreading rate between the collar and the pressure ring causes.
- the increase of the axial component then decreases progressively until the desired increase for the working range of the barrier effect is achieved and then remains constant until the end of the web
- For the rate of change is at ball grooves an initial angle range of 6 ° to 9 ° and an outlet angle of 1 ° to 1, 5 ° is proposed as appropriate, with the exit angle remaining constant until the end of the track
- the duration to overcome the clearance is small. Since the pitches of the intended ball grooves assume very low values, the axial adjustment path for actuating the fins of the friction arrangement is disadvantageously low.
- the present invention has for its object to make a device for axial adjustment of a lamellar switching element of the type mentioned in such a way that a fast and safe operation of the lamellar switching element is ensured and is easy to control.
- a device for axial adjustment of at least one lamellae switching element with a swivel wheel and a ball ramp disc adjacent thereto wherein the swivel wheel is axially fixed and rotatable and the ball ramp disc rotatably and axially displaceably mounted, and wherein the swivel wheel interacts with the ball ramp disc by means of rolling elements, which in depth-varying Grooves of the swivel wheel and arranged in corresponding grooves of the ball ramp disc, wherein the grooves have a variable pitch over their course.
- the grooves starting from an initial position of the rolling elements in the open state of the louver switching element in a first direction of movement of the pivot wheel, an initial pitch between 10 ° and 25 ° in a clearance range of the louver switching element and a pitch of at least 1, 3 ° to 1, 7 °, in a workspace of the louver switching element.
- the clearance of the lamellae switching element which may be a multi-plate clutch or a multi-disc brake, which advantageously very short operating times of the louver switching element can be achieved and an optimal combination of force and positioning time is reached.
- the grooves in an area adjacent to the clearance area in a second direction of movement of the pivot wheel, which is opposite to the first direction of movement, adjacent region have a slope of at least approximately zero.
- the means for axial adjustment for the operation of two lamellae switching elements may be provided, wherein the first direction of movement a first louver switching element closing and a second louver switching element opening Oreh Gayscardi of the swivel wheel and the second direction of movement is a rotational movement direction of the swivel wheel which opens the first slat selector element and closes the second selector element.
- the ball ramp disc and / or on the other hand the slidability of the slats limiting the support disc on its surface facing the slats formed with a cooperating with the slats friction lining
- the multi-disc brake running space is shortened and thus the package is optimized.
- the design of the ball ramp disc with a sintered material whereby the processing of the ball ramp disc can be limited to certain local areas.
- the manufacturing costs for the ball ramp disk fall in an advantageous manner from low.
- FIG. 1 shows a partially sectional schematic representation of a rear axle transmission unit of a motor vehicle with an operable by an electric motor device for axial adjustment of a lamellar switching element
- Figure 2 is a fragmentary schematic cross-sectional sketch of a groove of a ball ramp disc of the means for axial adjustment and a groove of a pivot wheel of the device for axial adjustment of Figure 1, wherein a guided ball on the ball ramp disc is shown in an initial position with the state of the lamellae switching element.
- Fig. 3 is a representation corresponding to Fig. 2 of the means for A- xialeingna, wherein the ball is shown in a transition state between an end of a clearance and a beginning of a working range of the lamellar switching element;
- Fig. 4 is an illustration of the axial adjustment device corresponding to Figs. 2 and 3 showing the ball in a state of the louver switching element in the work area;
- Fig. 6 is a fragmentary schematic cross-sectional sketch of the groove of a ball ramp disc and the groove of the pivot wheel of the means for axial adjustment of Fig. 5, wherein the ball is shown in a neutral position.
- a portion of a transmission unit 1 is shown, which is one of a drive engine or internal combustion engine 10 provided only, transmitted via a drive shaft 2 drive torque to a first output shaft 3 and a coaxial thereto and with respect to the drive shaft 2 symmetrically arranged second output shaft 5 distributed.
- the gear unit 1 is provided for installation in a motor vehicle and is designed in the embodiment shown as Schuachsgetriebetician, but it is also conceivable that a substantially analog gear unit is used as Vorderachsgetriebetician. It is likewise conceivable to use the present transmission unit both as a front-axle transmission unit and as a rear-axle transmission unit, for example in a four-wheel drive motor vehicle,
- the output shafts 3 and 5 which are rotatably mounted about a common longitudinal axis X are connected at their free ends in each case with a not-shown vehicle wheel, wherein viewed in the installed state of the Schuachsgetriebeisme 1, a vehicle wheel with respect to the first output shaft 3 on a vehicle in the front direction left transmission side 7 and a vehicle wheel with respect to the second output shaft 5 on a right transmission side 9 is located.
- the Hinterachsgetriebetician 1 includes a Get ⁇ ' ebe housing 11, which with a substantially surrounding the drive shaft 2 front gear housing part 12 with a left side of the transmission 7 associated side gear housing part 13, from which the first output shaft 3 protrudes laterally, and with a non-illustrated the right transmission side 9 associated side gear housing part, from which the second output shaft 5 protrudes laterally, is formed.
- the rear axle transmission unit 1 distributes the drive torque transmitted from the drive shaft 2 to the two output shafts 3 and 5 and can It also cause uneven Momentenvert ⁇ ilung on the two output shafts 3 and 5 and thus actively improve the driving characteristics.
- the drive torque is introduced from the drive shaft 2 in a differential unit 15 which is formed with a differential 17 and a differential cage 19 and connected to a device 14 for influencing the drive torque to the output shafts 3 and 5.
- a differential unit 15 which is formed with a differential 17 and a differential cage 19 and connected to a device 14 for influencing the drive torque to the output shafts 3 and 5.
- For operative connection between the drive shaft 2 and the differential cage 19 is fixedly connected to the drive shaft 2 drive pinion 21 with a fixed connected to the differential cage 19 ring gear 23 into engagement, wherein the differential cage 19 is rotatably mounted about the longitudinal axis X and in the transmission housing 11th supported.
- the differential 17 is formed in a manner known per se with two output-side bevel gears 25 and 27 connected to the respective output shaft 3 and 5 and with two bevel gears 29 and 31 meshing with the two bevel gears 25 and 27.
- the two drive-side bevel gears 29 and 31 are rotatably mounted on a bolt 33 which is fixed in the differential cage 19 with respect to a rotation about the longitudinal axis X.
- Fig. 1 shows two embodiments of the drive side bevel gears 29 and 31 and the cooperating output side bevel gears 25 and 27, which are each engaged with each other, the expert can select an alternative according to the particular application.
- the device 14 is designed to influence the drive torque on the output shafts 3 and 5 with two symmetrically arranged to the transmission center axis Y identically constructed torque vectoring units of the two torque vectoring units in Fig. 1, only the left side of the transmission. 7 associated torque vectoring unit 35 is shown. which will be described below.
- the torque vectoring units are arranged in the gear housing 11 and are in the present case continuously adjusted and actuated by a respective, switchable electric motor 37.
- this has a planetary gear set formed as a gear ratio stage 39 without a ring gear and an actuatable by the electric motor 37 brake device 51, wherein the translation stage 39 with two sun gears 61 and 63 currently-. is formed, of which a first sun gear 61 fixed to the differential cage 19 and of which a second sun gear 63 is fixedly connected to the output shaft 3.
- the sun gears 61 and 63 cooperate with present three rotatably mounted on a planetary carrier 65 planet, of which two planets 69 and 71 are visible, and which have a continuous toothing 73.
- the brake device 51 has a lamellae brake 77 designed as a lamellae.
- the with respect to their transfer capability infinitely adjustable multi-disc brake 77 has arranged as fins on the planet carrier 65 inner plates 75 which cooperate with defined in the gear housing 11 outer plates 79 by their axial adjustability such that they can be brought into a frictional or frictional contact.
- the electric motor 37 actuates the brake device 51 via an intermediate gear 85 which is driven by its drive shaft 83 and is fixed to the drive shaft 83 of the electric motor 37 and actuates a device 87 for axial adjustment of the multi-disc brake 77.
- the means 87 for axial adjustment of the multi-disc brake 77 is provided with a pivoting wheel 89, which is in engagement with the intermediate 85 and how the idler 85 is disposed on the side facing away from the transmission center axis Y side of the multi-disc brake 77, and one between the pivot wheel 89 and the multi-disc brake 77th arranged ball ramp plate 91 constructed
- the translation stage 39 runs around the longitudinal axis X without torque transmission. If a friction connection in the multi-disc brake 77 is triggered via the electric mofor 37, a torque vectoring torque acting on the respective output shaft 3 or 5 is generated from the drive torque. This is done by a support of the flat support 65 via the braking device 51 in the Transmission housing 11. It is thus a torque transmission from the drive shaft 2 via the differential cage 19 and from there by means of the planet carrier 65 from the first sun gear 61 to the respective connected to the output shaft 3 and 5 second sun gear 63 is generated by means of which a different torque distribution the first output shaft 3 and the second output shaft 5 can be achieved.
- the ball ramp disk 91 mounted in a rotationally fixed and axially displaceable manner in the gear housing 11 and the swivel wheel 89 have three grooves 93 which vary in depth about the first output shaft 3 of the axial adjustment device 87 over their radius.
- grooves 93 of the ball ramp disk 91 corresponding, also varying in depth grooves 95 of the pivot wheel 89 are three trained as balls 97 rolling elements, via which at a controlled by the electric motor 37 rotation of the pivot wheel 89, an axial movement of the ball ramp plate 91st results, so that the housing-fixed outer disk 79 after overcoming a clearance of the multi-disc brake 77 with the inner disk 75 of the multi-disc brake 77 enter into a friction joint.
- the maximum twist angle of the ball ramp disk 91 can be realized in an embodiment with three balls 97. Furthermore, by the use of only three balls 97 of the supporting portion per ball maximum, the load in relation to the number of balls due to manufacturing tolerances can not be increased by more balls. A maximum angle of rotation of the pivot wheel 89 thus has due to the present case with three balls 97 formed device 87 Axial setting a value of about 120 °. But it is also possible to use more balls,
- the grooves 93 of the ball ramp disc 91 which in the present case represents a component made of sintered material, and the grooves 95 of the pivot wheel 89 are shown in FIG. 2 in a cross section and have, starting from a starting position shown in this figure, in which the ball ramp disc 91 and the Pivoting wheel 89 have a minimum axial distance from each other, over a circumferential region which is assigned to an axial, Lsymmetricspiel Scheme 130 of the lamellae switching element 77 associated adjustment S1, a constant large pitch and a subsequent peripheral region, which a travel S2 of a work area 132 with a structure of Coupling torque is assigned to a constant small slope.
- the ball track sections of the clearance area 130 and the working area 132 are connected to each other via a radius 134.
- FIGS. 3 and 4 which shows the ball 97 in further stages during a rotation of the swivel wheel 89 in a first direction of movement I, which represents a rotational movement closing the multidisk brake 77, in the clearance play area 130
- the clearance of the multi-disc brake 77 can be overcome.
- the working area 132 has a relatively small pitch of 1.4 ° to 1.7 °, whereby the axial adjustment of the multi-disc brake 77 can be made very precisely and only a slight moment is applied to the electric motor 37 to build up a clutch torque.
- the clearance of the multi-disc brake 77 can be traversed quickly at a given maximum speed of the electric motor 37 and in the working area 132 a high positioning accuracy can be achieved with a high number of revolutions of the electric motor.
- a high number of revolutions of the electric motor 37 results in a good Position control, which is expediently formed with a sensor, not shown.
- the slope in the different regions 130, 132 can be selected depending on the required resolution such that an optimal path resolution is achieved on the electric motor 37 and that the non-linearity of friction linings of the fins 75, 79 of the multi-disc brake 77 is compensated, the slope is formed flatter with stiffer friction lining.
- the ball ramp disk 91 and an opposite support disk of the disk switching element 77 are provided with a friction lining, with which these elements serve as end disks of the disk switching element 77,
- Fig. 5 a largely the Schuachsgetriebetician of FIG. 1 corresponding Schuachsgetriebetician 1 is shown, which in contrast to the Schuachsgetriebetician of FIG. 1, only a single electric motor 37 ! for the control of both the torque vectoring unit 35 'of the vehicle front left side of the transmission 7 and the torque vectoring unit 36 of the vehicle front right side gear unit 9 associated with 87' for axial adjustment.
- the electric motor 37 ' engages with a connecting shaft 105 which, in turn, cooperates by means of an intermediate gear 85', 86 with a respective swivel wheel 89 'or 90 of the device 87' associated with an output shaft 3 or 5 for axial adjustment.
- FIGS. 6 shows by way of example the formation of the grooves 93 'of the ball ramp disk 91' and the pivot wheel 89 'on the first output shaft 3, wherein the ball ramp disk 92 and the pivot wheel 90 at the second Output shaft 5 are formed substantially identical.
- the electric motor 37 ' actuates in a direction of its drive shaft 83' in one direction, for example, the left side of the transmission 7 associated disc brake 77 'in the first direction of movement I and upon rotation of its drive shaft 83' in the other direction of the right transmission side 9 associated Multi-disc brake 77B by rotation of the pivot wheel 90 in an opposite direction of movement H.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Retarders (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006025061A DE102006025061A1 (de) | 2006-05-30 | 2006-05-30 | Einrichtung zur Axialeinstellung wenigstens eines Lamellenschaltelementes |
PCT/EP2007/055083 WO2007138002A1 (de) | 2006-05-30 | 2007-05-25 | Einrichtung zur axialeinstellung wenigstens eines lamellenschaltelementes |
Publications (1)
Publication Number | Publication Date |
---|---|
EP2021646A1 true EP2021646A1 (de) | 2009-02-11 |
Family
ID=38293341
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07729512A Withdrawn EP2021646A1 (de) | 2006-05-30 | 2007-05-25 | Einrichtung zur axialeinstellung wenigstens eines lamellenschaltelementes |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2021646A1 (de) |
DE (1) | DE102006025061A1 (de) |
WO (1) | WO2007138002A1 (de) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8231492B2 (en) | 2009-04-16 | 2012-07-31 | GM Global Technology Operations LLC | Torque transmitting device |
DE102009054878A1 (de) | 2009-12-17 | 2011-06-22 | ZF Friedrichshafen AG, 88046 | Axialverstelleinrichtung, beispielsweise für eine Kupplung eines Kraftfahrzeuges |
DE102009054879A1 (de) | 2009-12-17 | 2011-06-22 | ZF Friedrichshafen AG, 88046 | Axialverstelleinrichtung, beispielsweise für eine Kupplung eines Getriebes oder eine Differentialsperre eines Kraftfahrzeuges |
DE102010037317B4 (de) * | 2010-09-03 | 2017-05-04 | FEV Europe GmbH | Betätigungsvorrichtung für die Betätigung einer Kupplungsanordnung |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3909112A1 (de) * | 1988-05-05 | 1990-09-27 | Uni Cardan Ag | Ausgleichsgetriebe |
DE4007506C1 (de) * | 1990-03-09 | 1991-10-24 | Gkn Automotive Ag, 5200 Siegburg, De | |
US5019021A (en) * | 1990-07-02 | 1991-05-28 | Eaton Corporation | Modulating limited slip differential |
US6551209B2 (en) * | 2000-01-18 | 2003-04-22 | Eaton Corporation | Electronically actuated locking differential |
JP4446112B2 (ja) * | 2001-10-18 | 2010-04-07 | イートン コーポレーション | 差動ギア装置 |
US6571928B1 (en) * | 2001-12-21 | 2003-06-03 | Gkn Automotive, Inc. | Engagement mechanism with two stage ramp angle |
DE102005053555B3 (de) * | 2005-11-08 | 2007-08-02 | Gkn Driveline International Gmbh | Kugelrampenanordnung mit variabler Steigung der Kugelrillen |
-
2006
- 2006-05-30 DE DE102006025061A patent/DE102006025061A1/de not_active Withdrawn
-
2007
- 2007-05-25 EP EP07729512A patent/EP2021646A1/de not_active Withdrawn
- 2007-05-25 WO PCT/EP2007/055083 patent/WO2007138002A1/de active Application Filing
Non-Patent Citations (1)
Title |
---|
See references of WO2007138002A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2007138002A1 (de) | 2007-12-06 |
DE102006025061A1 (de) | 2007-12-06 |
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