CN101512175A - Self-adjusting friction clutch - Google Patents
Self-adjusting friction clutch Download PDFInfo
- Publication number
- CN101512175A CN101512175A CNA200780033427XA CN200780033427A CN101512175A CN 101512175 A CN101512175 A CN 101512175A CN A200780033427X A CNA200780033427X A CN A200780033427XA CN 200780033427 A CN200780033427 A CN 200780033427A CN 101512175 A CN101512175 A CN 101512175A
- Authority
- CN
- China
- Prior art keywords
- lever
- friction clutch
- worm gear
- spring
- spring lever
- 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.)
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Classifications
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- 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
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/75—Features relating to adjustment, e.g. slack adjusters
- F16D13/757—Features relating to adjustment, e.g. slack adjusters the adjusting device being located on or inside the clutch cover, e.g. acting on the diaphragm or on the pressure plate
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- 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
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/583—Diaphragm-springs, e.g. Belleville
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Friction clutch with a housing (12), a pressure plate (16) which is connected to the latter in a rotationally fixed manner but such that it is movable axially to a limited extent, a spring lever (22) which is provided between the housing and the pressure plate and has a plurality of lever elements (36), which are arranged in the manner of a ring, for actuating the friction clutch, wherein a radially outer circumferential extent of the spring lever can be changed as a consequence of an axial adjustment of a radially inner circumferential region (34) of the spring lever, and with a wear-adjusting device which is provided with a freewheel and, in the event of the circumferential extent being increased or reduced by an extent exceeding a predetermined extent, brings about a relative rotation between the spring lever and a component (56). As a consequence of said relative rotation, the relationship between the position of the spring lever and the position of the pressure plate changes to compensate for wear, wherein the wear-adjusting device contains a self-locking step-down gear (44, 46, 48, 52, 54) which converts a threshold-exceeding increase or decrease of the outer circumferential extent between the lever elements into a relative rotation between the spring lever and the component (56).
Description
Technical field
The present invention relates to a kind of friction clutch, this friction clutch has a housing and one and does not have the pressure strip that relatively rotates ground but can be connected with axial motion with this housing, wherein, between housing and pressure strip, be provided with the spring lever that to swing, can operate this friction clutch by means of this spring lever.This spring lever is ring discoid generally and is made up of a plurality of lever elements of arranging abreast each other in a circumferential direction.
Background technique
This friction clutch is for example known by DE 103 16 445 A1, DE 101 34 118 A1 and DE34 46 460 A1.In these open source literatures, especially described by external force being incorporated on the spring lever and friction clutch closed and that open by the spring lever unloading.In DE 103 16445 A1, additionally propose, the wearing and tearing that produce on the friction covering of clutch disk are compensated.
Summary of the invention
Task of the present invention is, so further structure starts described friction clutch, but make operation friction compensation sheet lining wearing and tearing by spring lever, the clutch torque characteristic curve is irrespectively kept in its length of life basically with the wearing and tearing of clutch to a great extent.
This task solves by a kind of friction clutch, and this friction clutch has: a housing; One is not had with this housing and to relatively rotate ground but pressure strip that can be axial restricted motion ground be connected; A spring lever that is arranged between housing and the pressure strip, this spring lever has a plurality of lever elements of arranging annularly, be used to operate this friction clutch, wherein, the circumferential size of the radially outer of spring lever can change owing to the axial displacement of the inner radial circumferential area of spring lever; An abrasion adjustment that is provided with idling device, this abrasion adjustment causes relatively rotating between spring lever and the member in the increase of circumferential size or when reducing to surpass a pre-size of determining, because this relatively rotates, change on the meaning that is configured in compensate for wear between the position of spring lever and the position of pressure strip, wherein, abrasion adjustment comprises the speed reduction gearing of a self-locking, and the speed reduction gearing of this self-locking is with the increase that surpasses threshold value of the circumferential size between the lever element or reduce to convert to relative reversing between spring lever and this member.
Speed reduction gearing advantageously has one and is bearing in a worm gear on the lever element, this worm gear is configured with circumferential teeth portion, one is configured in a cooperation tooth portion on the spring arm and is engaged in this circumferential teeth portion, this spring arm is fixed on another lever element, wherein, this tooth portion constructs like this, only makes when the increase of the circumferential distance of the outside between the lever element or just carries out reversing of worm gear when reducing above threshold value.
Worm gear advantageously has helical flute on it is distolateral and its rotation axis points to like this, makes helical flute only be engaged on one in a side of rotation axis and is configured in housing and does not have in the cooperation tooth portion on the member that is connected with relatively rotating.
For high reduction speed ratio additionally advantageously, the diameter of the outer toothed portion of worm gear is greater than the diameter of helical flute.
Further advantageously, this friction clutch is constructed like this, make to cooperate tooth portion roughly extend diametrically and roughly be arranged on last to the identical distance of the distance of the mid point of spring lever with the rotation axis of worm gear.
Worm gear for example can be bearing on the leaf spring arm that is fixed on the affiliated lever element, and this leaf spring arm forces helical flute and cooperates the engagement of tooth portion.
Helical flute and affiliated cooperation tooth cage structure have rectangular cross section.
Be applied to component that the power on the worm gear works in a circumferential direction advantageously with respect to oppositely pointing to by spring arm by the component that cooperates the tooth portion power on the helical flute that acts on to work in a circumferential direction.
Worm gear can be configured to sintered part or the cold-extruded part through sclerosis.
Description of drawings
By means of schematic accompanying drawing the present invention is described exemplarily and in more detail below.Accompanying drawing is represented:
The principle semi-section of Fig. 1 friction clutch,
Fig. 2 is according to the plan view of spring lever of the present invention,
Fig. 3 is according to the cross section view of the III-III of Fig. 2, and
Fig. 4 is according to the cross section view of the IV-IV of Fig. 2,
Embodiment
Fig. 1 shows one always with the semi-section of the friction clutch of 10 marks, and this friction clutch can rotate around an axis A-A.This friction clutch has a housing 12 or a lid that is configured to anchor pole with known manner, and this housing maybe this lid for example is fixedly connected by being threaded or riveting with a back-pressure plate 14.Pressure strip 16 and the housing 12 that is configured to the plate lid do not have and relatively rotate ground but can be connected to axial restricted displacement.This connection for example can realize by means of the leaf spring coupling device.Between pressure strip 16 and back-pressure plate 14, can clamp the friction covering 18 of clutch disk 20.Clutch disk 20 is connected so that transmitting torque with known manner with a transmission output shaft 22.
The spring lever 22 of the ring discoid of forming by some lever elements generally be supported on the housing 12 at its excircle 24 places and within it circumference 26 places cooperate with a control member 28, this control member for example is connected with an actuator or a clutch pedal by a bearing concentric with respect to rotation axis A-A.
According to the position of the member of Fig. 1 separation or open mode corresponding to clutch.The position of drawing with dotted line of spring lever 22 is corresponding to the operating position of clutch, pressure strip 16 is pressed to back-pressure plate 14 by spring lever 22 in this operating position, thus, clutch disk 20 rotates with back-pressure plate 14, and this back-pressure plate for example can be the constituent element of the flywheel of explosive motor.
As mentioned above, be expressed in its closed state by control member 28 according to the clutch of Fig. 1 and be arranged in its open position as the time spent in that control member is unable.Spring lever 22 always constitutes the member of a belleville spring form, and the member of this belleville spring form taper ground by control member 28 operation the time is out of shape and for example is arranged in its original state at least approx when clutch is opened.
When friction covering 18 wearing and tearing or clutch other parts show wearing and tearing along with the growth of run duration, in order to make clutch closed fully, control member 28 must move further, and in other words, spring lever 22 must the distortion of taper ground surpass the position of drawing with dotted line.In order to compensate this wearing and tearing, in other words, even in order to make clutch under abrasion condition, also have open position according to Fig. 1, spring lever 22 with respect to pressure strip 16 around axis A-A and reverse with respect to slope 30 thus, gapless distance when thus, between spring lever 22 and pressure strip 16, forming in spring lever 22 is in according to the position of Fig. 1 owing to the axial gradient of slope.
Describe abrasion adjustment by means of Fig. 2 to Fig. 4 below, this abrasion adjustment is always used 34 marks in Fig. 2.
Fig. 2 shows in Fig. 1 not the plan view of the spring lever of representing with the details of Fig. 2 to Fig. 4 22.Fig. 3 shows along the section of the III-III of Fig. 2, and Fig. 4 shows along the section of the line IV-IV of Fig. 2.
As especially from Fig. 2 appreciable, spring lever 22 is made up of some lever segments or lever element 36, these lever segments or lever element are arranged in a circumferential direction each other abreast, wherein, adjacent lever element 36 upwards was connected to each other by connecting element 38 in week, in an example shown, these connecting element respectively are configured to one with a lever element 36 and for example rivet with other connecting element.Connecting element 38 is configured to crooked like this, makes these connecting element especially allow relative movement in a circumferential direction between the lever element.Lever element 36 has always constituted the spring lever 22 that is configured to the belleville spring form with connecting element 38, and as shown in fig. 1, this spring lever is supported at its excircle place on the housing 12 of friction clutch and with its inner circumference and cooperates with control member 28.Outer circumferential area along lever element 36 constitutes slit 40 between lever element, decide on the taper distortion of spring lever 22, and these slits broaden by means of control member 28 or narrow down.
Should suppose in an example shown: the width in slit 40 diminishes when the inner circumference of spring lever 22 moves right according to Fig. 1.When control member 28 move right to when surpassing on the position of rest of clutch open position from position according to Fig. 1 or spring lever 22 because too much wearing and tearing unable time spent, the width minimums done fully that become of friction covering 18.
According to the present invention, leaf spring that is configured to leaf spring arm 42 for example is connected rigidly by one in riveted joint and the lever element 36, and a worm gear 44 is rotatably supported on the free end of this leaf spring arm.Worm gear 44 is configured with a circumferential teeth portion 46, cooperation tooth portion 48 on end that is configured in spring arm 50 is engaged in this circumferential teeth portion, in an example shown, this spring arm is connected with the outer circumferential area that is not directly adjacent with the lever element that is provided with leaf spring arm 42 lever element 36.Cooperate tooth portion 48 to comprise at least one tooth and constitute a ratchet, the locking and on another direction " idle running " in one direction of this ratchet with spring arm 50.
For this reason, construct spring arm 50 like this, make this spring arm impel and cooperate tooth portion 48 to be engaged in the circumferential teeth portion 46.Formed tooth portion 46 and 48 make to cooperate tooth portion 48 that worm gear 34 is rotated in the counterclockwise direction in according to example shown in Figure 2, but worm gear 44 rotation in the clockwise direction is not to carry out forcibly, but these tooth portions can cross mutually at this like this.
As appreciable from Fig. 3 and Fig. 4, worm gear 44 its downsides are provided with the helical flute 52 of spiral extension.Worm gear 44 can be bearing in the leaf spring arm 42 rotationally around axis B-B, this axis B-B tilts like this with respect to circumferencial direction, make being arranged in of two zones on the circumferencial direction with respect to rotation axis B-B and being engaged on the tooth portion 54 that cooperates of helical flute 52 only, the tooth radial finger of this cooperation tooth portion to and this cooperation tooth cage structure one with member 56 that housing 12 is connected rigidly in or be configured in this housing originally on one's body.
The function of abrasion adjustment 34 is as follows:
Suppose: when spring lever 22 when position shown in Fig. 1 dotted line moves to shown in the continuous lines the position or surpass position shown in the continuous lines for Compensation Regulation clutch on purpose and exceed a pre-size of determining to the right, the length of the excircle 24 of distance between the slit 40 or spring lever 22 reduces.When this size or this threshold value surpass the modulus of tooth portion 46,48, cooperate tooth portion 48 to cross circumferential teeth portion 46 left according to Fig. 2, thus, worm gear 44 reverses in the counterclockwise direction in the time of in spring lever then turns back to according to the position of Fig. 1.Cooperate in the tooth portion 54 because helical flute 52 is engaged on---wherein this engagement guarantees by the corresponding prestressing of leaf spring arm 42, so this cause spring lever 22 with and the member 56 fixed of housing or housing 12 between relative reverse and also cause thus spring lever 22 and nothing relatively rotate and the pressure strip 16 that is connected of housing 12 between reverse relatively.Slope 30 is moved with respect to spring lever 22, make the wearing and tearing that produced be compensated adjusting thus.
With worm gear 44 axially be expressed to the leaf spring arm 42 that cooperates in the tooth portion 54 between housing and ring discoid spring also transmission reverse required torque.
Though helical flute 52 is self-locking with cooperating the engagement between the tooth portion 54, advantageously, in order to improve friction torque, worm gear 44 is provided with an additional rubbing device facing to leaf spring arm 42, for example spring sheet or similar device.
The sense of rotation of worm gear 44 is advantageously such, makes to be applied to component that the power on the worm gear 44 works in a circumferential direction with respect to oppositely being pointed to by the component that cooperates tooth portion 54 power on the helical flute 52 that act on to work in a circumferential direction by spring arm 50.In the bearing device of worm gear, only must support the poor of ratchet power and the power that causes by helical tooth portion thus.In other words: advantageously stretch with the force direction that cooperates tooth portion 48 to constitute the spring arm 50 of ratchet spring, make the bearing device unloading of worm gear 44 on leaf spring arm 42 thus against the sense of rotation of spring lever.
Advantageously, worm gear 44 is configured to sintered part or cold-extruded part and through sclerosis.
In the present invention of exemplary description, a member (ratchet) is on the pre-tangential direction of determining or the speed reduction gearing that moves through self-locking that carries out in a circumferential direction is transformed into reversing relatively of two members (arm spring and member 56) and convert to by slope and to move axially, and the present invention can carry out multiple modification.
The reference number inventory
10 friction clutches, 36 lever elements
12 housings, 38 Connection Elements
14 back-pressure plates, 40 slits
16 pressure strips, 42 leaf spring arms
18 friction coverings, 44 worm gears
20 clutch disks, 46 circumferential teeth portions
22 spring levers 48 cooperate tooth portion
24 excircles, 50 spring arms
26 inner circumferences, 52 helical flutes
28 control members 54 cooperate tooth portion
30 slopes, 56 members
34 abrasion adjustments
Claims (9)
1. friction clutch, this friction clutch has: a housing (12); One is not had with this housing and to relatively rotate ground but pressure strip (16) that can be axial restricted motion ground be connected; A spring lever (22) that is arranged between this housing and this pressure strip, this spring lever has a plurality of lever elements of arranging annularly (36), be used to operate this friction clutch, wherein, the circumferential size of the radially outer of this spring lever can change owing to the axial displacement of the inner radial circumferential area (26) of this spring lever; An abrasion adjustment (34) that is provided with idling device, this abrasion adjustment causes relatively rotating between this spring lever and the member (56) in the increase of this circumferential size or when reducing to surpass a pre-size of determining, because this relatively rotates, change on the meaning that is configured in compensate for wear between the position of this spring lever and the position of this pressure strip, wherein, this abrasion adjustment comprises the speed reduction gearing (44 of a self-locking, 46,48,52,54), the speed reduction gearing of this self-locking is with the increase that surpasses threshold value of the circumferential size between these lever elements (36) or reduce to convert to relative reversing between this spring lever (22) and this member (56).
2. according to the friction clutch of claim 1, wherein, this speed reduction gearing has a worm gear (44) that is bearing on the lever element (36), this worm gear is configured with circumferential teeth portion (46), a cooperation tooth portion (48) that is configured on the spring arm (50) is engaged in this circumferential teeth portion, this spring arm is fixed on another lever element, wherein, described tooth portion constructs like this, only makes when the increase of the circumferential distance of the outside between these lever elements or just carries out reversing of this worm gear when reducing above threshold value.
3. according to the friction clutch of claim 2, wherein, this worm gear (44) has helical flute (52) on it is distolateral and its rotation axis (B-B) points to like this, makes this helical flute only be engaged in the cooperation tooth portion (54) that is configured on this member (56) in a side of this rotation axis.
4. according to the friction clutch of claim 3, wherein, the diameter of the circumferential teeth portion (46) of this worm gear (44) is greater than the diameter of this helical flute (52).
5. according to the friction clutch of claim 3 or 4, wherein, this cooperation tooth portion (54) roughly extends diametrically and roughly is arranged on last to the identical distance of the distance of the mid point of this spring lever (22) with the rotation axis (B-B) of this worm gear (44).
6. according to the friction clutch of claim 3 or 4, wherein, this worm gear (44) is bearing on the leaf spring arm (42) that is fixed on the affiliated lever element (36), and this leaf spring arm forces this helical flute (52) to cooperate tooth portion (54) engagement with this.
7. according to the friction clutch of one of claim 3 to 6, wherein, this helical flute (52) and affiliated cooperation tooth portion (54) are configured with rectangular cross section.
8. according to the friction clutch of one of claim 3 to 7, wherein, being applied to the component that the power on this worm gear (44) works in a circumferential direction by this spring arm (50) oppositely points to respect to the component that is worked in a circumferential direction by this cooperation tooth portion (54) power on this helical flute (52) that acts on.
9. according to the friction clutch of one of claim 2 to 8, wherein, this worm gear (44) is configured to sintered part or the cold-extruded part through sclerosis.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102006042435.2 | 2006-09-09 | ||
| DE102006042435 | 2006-09-09 | ||
| PCT/DE2007/001375 WO2008028448A1 (en) | 2006-09-09 | 2007-08-01 | Self-adjusting friction clutch |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101512175A true CN101512175A (en) | 2009-08-19 |
| CN101512175B CN101512175B (en) | 2011-06-22 |
Family
ID=38657690
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200780033427XA Expired - Fee Related CN101512175B (en) | 2006-09-09 | 2007-08-01 | Self-compensation adjusting friction clutch |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN101512175B (en) |
| DE (1) | DE112007001691B4 (en) |
| WO (1) | WO2008028448A1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103221707A (en) * | 2010-11-19 | 2013-07-24 | 舍弗勒技术股份两合公司 | Clutch device |
| CN105934597A (en) * | 2014-01-15 | 2016-09-07 | 舍弗勒技术股份两合公司 | Self-adjusting clutch with adjusting display/feedback |
| CN107575501A (en) * | 2016-05-02 | 2018-01-12 | 法雷奥离合器公司 | Wear compensation type clutch mechanism |
| CN112739925A (en) * | 2018-09-13 | 2021-04-30 | 伊顿智能动力有限公司 | Clutch modulation system with anti-backdrive wear feature |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009014001B4 (en) | 2008-04-10 | 2018-07-26 | Schaeffler Technologies AG & Co. KG | Friction clutch with adjuster |
| DE102010021723A1 (en) | 2009-06-25 | 2010-12-30 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Clutch assembly for use in dual-clutch transmission, has sensor springs performing tangential movement based on axial distance of lever systems, driving worm wheel by ratchet and including linear characteristic curves |
| DE102010024924A1 (en) | 2009-07-16 | 2011-01-20 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Friction clutch for motor vehicle, has stop formed on slider linearly shifted depending on axial pressurization of lever and driven against effect of energy storage of joint connected firmly with another lever |
| DE102010032672A1 (en) | 2009-08-31 | 2011-03-03 | Schaeffler Technologies Gmbh & Co. Kg | Lever engagement element for actuating friction clutch for dual clutch transmission, has pressurization surface transferred with minimum force, which is adjustable independent of maximum force and smaller than counter force at start point |
| DE102014208209A1 (en) * | 2013-05-29 | 2014-12-04 | Schaeffler Technologies Gmbh & Co. Kg | Sliding element for an adjusting device of a friction clutch |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3446460A1 (en) | 1984-12-20 | 1986-07-03 | Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart | DOUBLE CLUTCH FOR A MOTOR VEHICLE TRANSMISSION |
| ES2119668B1 (en) * | 1994-12-24 | 1999-04-01 | Fichtel & Sachs Ag | FRICTION CLUTCH WITH AUXILIARY SPRING TO ASSIST THE STRUT-OFF FORCE. |
| WO1999040335A1 (en) * | 1998-02-05 | 1999-08-12 | Valeo | Friction clutch mechanism, in particular for motor vehicle, comprising a wear take-up device |
| DE10134118B4 (en) | 2001-07-13 | 2013-02-21 | Volkswagen Ag | Double coupling |
| EP1710461A3 (en) * | 2002-04-10 | 2008-08-06 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Clutch device |
| ATE363607T1 (en) * | 2004-02-24 | 2007-06-15 | Luk Lamellen & Kupplungsbau | SELF-ADJUSTING CLUTCH |
| DE502006005343D1 (en) * | 2005-04-08 | 2009-12-24 | Luk Lamellen & Kupplungsbau | FRICTION CLUTCH |
-
2007
- 2007-08-01 CN CN200780033427XA patent/CN101512175B/en not_active Expired - Fee Related
- 2007-08-01 WO PCT/DE2007/001375 patent/WO2008028448A1/en active Application Filing
- 2007-08-01 DE DE112007001691.4T patent/DE112007001691B4/en not_active Expired - Fee Related
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103221707A (en) * | 2010-11-19 | 2013-07-24 | 舍弗勒技术股份两合公司 | Clutch device |
| CN103221707B (en) * | 2010-11-19 | 2016-04-06 | 舍弗勒技术股份两合公司 | Clutch device |
| CN105934597A (en) * | 2014-01-15 | 2016-09-07 | 舍弗勒技术股份两合公司 | Self-adjusting clutch with adjusting display/feedback |
| CN105934597B (en) * | 2014-01-15 | 2018-09-07 | 舍弗勒技术股份两合公司 | With adjusting display/adjusting feedback, self compensation adjustable type clutch |
| CN107575501A (en) * | 2016-05-02 | 2018-01-12 | 法雷奥离合器公司 | Wear compensation type clutch mechanism |
| CN107575501B (en) * | 2016-05-02 | 2020-10-23 | 法雷奥离合器公司 | Wear-compensating clutch mechanism |
| CN112739925A (en) * | 2018-09-13 | 2021-04-30 | 伊顿智能动力有限公司 | Clutch modulation system with anti-backdrive wear feature |
| CN112739925B (en) * | 2018-09-13 | 2023-07-14 | 伊顿智能动力有限公司 | Clutch modulation system with wear-resistant feature for reverse drive prevention |
Also Published As
| Publication number | Publication date |
|---|---|
| DE112007001691A5 (en) | 2009-04-23 |
| CN101512175B (en) | 2011-06-22 |
| WO2008028448A1 (en) | 2008-03-13 |
| DE112007001691B4 (en) | 2016-11-10 |
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| ASS | Succession or assignment of patent right |
Owner name: LUKOIL ASSET MANAGEMENT CO., LTD. Free format text: FORMER OWNER: LUK LAMELLEN UND KUPPLUNGSBAU GMBH Effective date: 20110415 |
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| C41 | Transfer of patent application or patent right or utility model | ||
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Effective date of registration: 20110415 Address after: German Boer Applicant after: Luk Lamellen & Kupplungsbau Address before: German Boer Applicant before: Luk Lamellen Und Kupplungsbau GmbH |
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Address after: German Herzogenaurach Patentee after: Schaeffler Technologies GmbH & Co. KG Address before: German Herzogenaurach Patentee before: Schaeffler Technologies GmbH |
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| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20110622 Termination date: 20180801 |