WO2011003386A1 - Doppelkupplung - Google Patents
Doppelkupplung Download PDFInfo
- Publication number
- WO2011003386A1 WO2011003386A1 PCT/DE2010/000743 DE2010000743W WO2011003386A1 WO 2011003386 A1 WO2011003386 A1 WO 2011003386A1 DE 2010000743 W DE2010000743 W DE 2010000743W WO 2011003386 A1 WO2011003386 A1 WO 2011003386A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- lever
- clutch
- friction clutch
- friction
- drive
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
-
- 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
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
- F16D2021/0607—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate
-
- 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
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
- F16D2023/126—Actuation by rocker lever; Rocker levers therefor
Definitions
- the invention relates to a double clutch with a first, drawn by a first lever actuator friction clutch and a second, pressed by a second lever actuator friction clutch.
- a generic lever actuator is known for example from DE 2004 009 832 A1.
- a one-sided clamped by means of a helical compression spring, a L Lucassprofil ist exhibiting lever is acted upon by a radially displaceable bearing block, which is supported on a base plate, so that upon the displacement of the bearing block a varying fulcrum formed and the lever on the clamped side opposite the lever end axially displaced from the position of the bearing block and, depending on the design of the friction clutch as a depressed or pressed-friction clutch applied to an engagement or release bearing and thereby actuates the friction clutch.
- the bearing block is radially displaced by an electric drive such as electric motor via a spindle.
- the object of the invention is therefore to propose a double clutch with lever actuators whose operation can be done reliably with low actuation forces and reliably fulfills the usual safety requirements.
- the object is achieved by a double clutch with a first, drawn by a first lever actuator friction clutch and a second, pressed by a second lever actuator friction clutch, wherein the lever actuators each have a spring loaded lever on one side, the lever tips by means of a radially to the axis of rotation of the friction clutches along a profiling the lever displaced and thus a variable contact point of the lever between a fixed base plate and the lever adjusting bearing block are moved to act on actuation bearings of the friction clutches, the bearing block is actuated by means of a drive automatically controlled by a control unit in at least one of the radial directions of motion and the drive kraftbeaufschlagt each lever actuator is formed from each fluidic actuator unit, in each case a displaceable in a fixed housing piston by means of a piston rod with the Lagerb Fluidic means here
- a pneumatic adjusting device By driving the linearly displaced bearing block by the linear piston movement of the piston of the fluidic actuator unit by means of the piston rod, a low-loss operation of the lever actuators can be proposed, which is not affected by the efficiency losses of spindle gear and carries the risk of jamming.
- a compressed air supply device is available anyway in a vehicle, as is the case with commercial vehicles for example, the equipment of the lever actuators with actuators made of pneumatic actuator units is not significant, since these are simple to manufacture and easy to actuate via control valves. Furthermore, the space requirement compared to the use of electric motors as drive at least neutral.
- a unilaterally pressurized piston actuator unit for a lever actuator wherein the piston is displaced axially against the action of a restoring force by a varied in a pressure chamber in communication with the piston pressure.
- This restoring force can be, for example, the spring acting upon the lever of the lever actuator and / or a restoring force of the lever spring or plate spring of the friction clutch acted upon by the lever via the actuating bearing.
- the pneumatic or hydraulic actuator unit can apply force to the bearing block in both directions and move radially, so that the friction clutch can be actively closed and opened or additionally supports the non-moving direction and / or a Self-locking generates and / or the bearing block and thus the friction clutch with respect to its degree of opening can be kept at any point of the clutch travel.
- at least one piston of the actuator unit of a lever actuator in both radial directions of movement can be arranged so that it can be displaced axially by a pressure varied in one of two pressure chambers which are in each case connected to one end face of the piston.
- This means that the piston can be pressurized on both sides with pressure in each case one pressure line.
- the control of these pressures can be done via a corresponding pneumatic or hydraulic control valve, which can connect one or both pressure ports to the pressure supply device, such as a pump and / or a compressed air reservoir / hydraulic medium storage.
- the lever actuator for actuating the drawn friction clutch is arranged on the other side of the counter-pressure plate, so that their pressure plate is pulled by means of the counter-pressure plate encompassing tie rods, so that both lever actuators in a space of the clutch bell at almost the same height and axially on the Scope offset between the geared components of the dual clutch transmission can be accommodated almost space neutral.
- the support of the actuating forces takes place in each case on the transmission housing, wherein the force directions are in opposite directions, the force receptacles of the lever actuators are therefore arranged in each case reversed.
- An advantageous embodiment of a dual clutch provides that both friction clutches open automatically with force-free drive (normally open).
- two pneumatic or hydraulic actuator units with only one side with pressure (air pressure / hydraulic pressure) acted upon pistons are provided for both friction clutches, which is displaced against the spring forces for independent opening of the friction clutches by means of pressure and closes the respective friction clutch.
- air pressure / hydraulic pressure air pressure / hydraulic pressure
- a blocking of the dual clutch transmission can be prevented when the other lever actuator is de-energized.
- the closed friction clutches must be kept permanently closed by applying pressure to the control units.
- the opposite embodiment provides to close both friction clutches in the power-free state of their drives or to keep closed (normally closed).
- the friction clutches are pressed by means of a corresponding design of their lever or disc springs and opened against the action of these closing forces of the lever actuators and their pneumatic / hydraulic drives.
- a pneumatic or hydraulic actuator unit for a friction clutch is also sufficient in each case, which can be acted upon with pressure in a single direction, namely the opening direction of the friction clutch.
- the friction clutches can be operated in this state without additional energy in the closed state.
- a friction clutch must always be kept open under pressure when driving.
- the safety concept is based on a low probability of double errors, so that when a lever actuator defect, the second lever actuator can always disengage its associated friction clutch and therefore a blocking of the dual clutch transmission in case both friction clutches transmit torque in each engaged in the respective part drive train.
- at least one gear of a partial drive train can be forcibly deployed.
- Two further embodiments provide to open the first friction clutch in the power-free state of their drive independently and to close the second friction clutch in the power-free state of their drive or vice versa.
- each pneumatic or hydraulic actuator units with a one-sided pressurizable piston are sufficient. If a lever actuator or friction clutch fails, the forcibly closed (normally closed) friction clutch automatically disengages, jams it and the forcibly opened friction clutch (normally closed) is opened by pneumatic operation.
- one or both friction clutches or their associated lever actuators can be self-holding or their movement can be frozen at each waypoint of the clutch travel (normally stack).
- the lever actuators one or both friction clutches are equipped with a pneumatic or hydraulic actuator unit whose piston is acted upon by pressure on both sides, so that by means of a balanced pressure in both pressure chambers of the piston and thus the bearing block and the lever with the lever tips with the Actuator and the lever tips of the lever spring of the respective friction clutch and thus the degree of transmission of torque on the friction clutch itself can be maintained. If both pressure chambers - leak tightness - isolated from the pressure source, this coupling state is frozen.
- each or both friction clutches can be operated in this way but also only a friction clutch, while the other is a self-opening or self-closing friction clutch operated with a bidirectional actuator unit in this way or can only have a one-sided control unit , Furthermore, one or both in this way operated friction clutches in non-energized state can be closing or opening friction clutches or both friction clutch can be provided in a mixed arrangement - one automatically closing and the other self-opening.
- Figure 1 is a schematic representation of a dual clutch with two lever actuators and one in the power-free state open drawn and a power-free
- FIG. 2 shows a schematic illustration of a double clutch with two lever actuators and a trailed friction clutch closed in the force-free state and a friction clutch which is open in the force-free state
- Figure 3 is a schematic representation of a double clutch with two lever actuators with a pulled and pressed, each self-holding in each position
- FIG. 4 shows a schematic illustration of a double clutch with two lever actuators and one pulled and one pressed friction clutch, each open in the force-free state
- Figure 5 is a schematic representation of a dual clutch with two lever actuators and a pulled and a depressed, each in the power-free state closed friction clutch,
- FIG. 6 is a schematic representation of a double clutch with two lever actuators and a self-holding pulled and a depressed, open in power-free state friction clutch
- FIG. 7 is a schematic representation of a double clutch with two lever actuators and a pulled, closed in the power-free state and a self-holding depressed friction clutch
- Figure 8 is a schematic representation of a dual clutch with two lever actuators and a self-holding pulled and closed in an off-state depressed friction clutch
- Figure 9 is a schematic representation of a dual clutch with two lever actuators and an open in power-free state pulled and a self-holding pressed friction clutch.
- the embodiment of the double clutch 1 shown in Figure 1 is common as a so-called three-disc clutch.
- the two friction clutches 2, 3 have the centrally arranged counter-pressure plate 4 together, wherein the friction clutch 2 is pulled by means of the counter-pressure plate 4 radially overlapping tie rod 5 and the friction clutch 3 is a depressed friction clutch.
- the pressure plates 6, 7 are axially displaceable and rotatably received by means not shown leaf springs on the fixedly connected to the counter-pressure plate 4 housing 8 and brace to close the friction clutches 2, 3, the friction linings of each with a transmission input shaft of a partial driveline of a dual clutch transmission rotationally connected clutch discs 9, 10 against the counter-pressure plate 4 to form a frictional connection.
- open or self-holding friction clutches brace the lever springs 11, 12, the friction clutches 2, 3 different.
- the present teaching could also be applied to a four-disc clutch, as can be taken in particular from EP 1 524 446 B1.
- the friction clutch 2 is open in the power-free state, that is, the lever spring 11 clamped via the tie rods 5, the pressure plate 6 against the counter-pressure plate 4 only when these of the lever actuator 13 for closing, that is to form a Reibschlus- Ses between the pressure plate 6 and counter-pressure plate 4 on the one hand and the friction linings of the clutch disc 9 on the other hand is pulled by the lever spring 11 is supported by a displacement of the lever tips on the housing 8 and produces a frictional engagement with the clutch disc 9.
- the lever actuators 13, 14 for the two friction clutches 2, 3 have a lever 15, 16, the lever tips 17, 18 via the rotational decoupling of the actuating bearings 29, 30 act directly on the lever tips of the lever springs 11, 12 axially and shift them.
- the displacement of the lever tips 17, 18 of the levers 15, 16 takes place by means of a one-sided, elastic clamping of the levers 15, 16 by means of the energy storage 19, 20 and the radial displacement of the lever points 21, 22 along a fixed housing fixed base plate 23, 24 by means of the bearing block 25, 26.
- a desired displacement of the lever tips for actuating the friction clutches 2, 3 is achieved with a displacement of the bearing blocks 25, 26.
- the friction clutch 2 is closed by a radially inward axially expanded profiling 27 when the bearing block 25 is displaced radially outward.
- the lever 15 is supported on the energy storage 19 and the changing fulcrum 21, whereby the lever tips 17 press the hinged to the lever tips of the lever spring 11 actuating bearing 29 in the direction of friction clutch 2, so that after deflection of the lever spring 11 on the housing 8 of this the tie rods 5 are actuated, which pull the pressure plate 6 against the counter-pressure plate 4 and close the friction clutch 2.
- the friction clutch 3 is opened by a radially inwardly axially opposite the base plate 24 narrowed profiling 28 when the bearing block 26 is displaced radially outward.
- the lever 16 is supported elastically on the energy store 20 and on the changing fulcrum 22, so that when the bearing block is displaced radially outward, the lever tips 18 tilt and the actuating bearing 30 moves away from the friction clutch 3. move and thus release the bias of the lever spring 12 for clamping the pressure plate 7, so that the friction clutch 3 is disengaged.
- the piston 35, 36 is connected by means of a piston rod 41, 42 with the bearing block 25, 26, so that a simple power transmission without additional efficiency-reducing gear or direction of rotation converter is made possible, as is required for example when using electric motors as a drive.
- the bearing block shown in dashed lines represents the closed coupling for the friction clutch 2 and the open state for the friction clutch 3. In this case, the pistons 35, 36 of the actuator units 31, 32 are displaced maximally axially by means of the pressure applied in the pressure chambers 37, 38.
- Figure 2 shows, in contrast to Figure 1, the dual clutch 101 in a modified
- FIG. 3 shows the dual clutch 201 with two self-retaining friction clutches 202, 203.
- the two control units 231, 232 in both displacement directions of the bearing blocks 225, 226 with pressure can be acted upon and have this in the housing 233, 234 axially displaceable piston 235, 236, which communicates with two pressurizable pressure chambers 237, 243 and 238, 244 in conjunction and with appropriate pressurization by the pressure supply means 245 and control by the control valve 246 and 247 in each position by setting corresponding differential pressures between the two pressure chambers 237th , 243 or 238, 244 can be set self-holding in each path position.
- the friction clutches 202, 203 are self-adjusting adjustable at each Kupplungswegposition. A coupling position can therefore be virtually frozen.
- the friction clutch 202 is closed in the radially outer position of the bearing block 225 and the friction clutch 203 in the radially outer position of the bearing block 226 is open. Accordingly, the friction clutch 202 is opened at a displacement of the bearing block 225 radially inward and the friction clutch 203 is closed at a displacement of the bearing block 226 radially inward.
- FIG. 4 shows the dual clutch 301, which is similar to the double clutches 1, 101 of FIGS. 1 and 2, with the difference that both friction clutches 302, 303 are open in the force-free state.
- the friction clutch 302 together with the lever actuator 313 substantially corresponds to the friction clutch 2 with the lever actuator 13 of FIG. 1 and the friction clutch 303 with the lever actuator 314 essentially corresponds to the friction clutch 103 with the lever actuator 114 of FIG.
- FIG. 5 shows the double clutch 401 similar to the dual clutches 1, 101 of FIGS. 1 and 2, with the difference that both friction clutches 402, 403 are closed in the force-free state.
- the friction clutch 402 together with the lever actuator 413 essentially corresponds to the friction clutch 102 with the lever actuator 113 of FIG. 2 and the FIGS Friction clutch 403 with the lever actuator 414 substantially the friction clutch 3 with the lever actuator 14 of Figure 1.
- FIG. 6 shows that similar to the double clutches 101, 201 of FIGS. 2 and 3
- Double clutch 501 with the difference that the friction clutch 502 a self-holding friction clutch and the friction clutch 503 is open in the power-free state.
- the friction clutch 502 together with the lever actuator 513 substantially corresponds to the friction clutch 202 with the lever actuator 213 of FIG. 2 and the friction clutch 503 with the lever actuator 514 substantially corresponds to the friction clutch 103 with the lever actuator 114 of FIG.
- FIG. 7 shows that similar to the double clutches 101, 201 of FIGS. 2 and 3
- the friction clutch 602 together with the lever actuator 613 essentially corresponds to the friction clutch 102 with the lever actuator 113 of FIG. 2 and the friction clutch 603 with the lever actuator 614 substantially corresponds to the friction clutch 203 with the lever actuator 214 of FIG.
- FIG. 8 shows the dual clutch 701, which is similar to the double clutches 1, 201 of FIGS. 1 and 3, with the difference that the friction clutch 702 is a self-holding friction clutch and the friction clutch 703 is closed in the force-free state.
- the friction clutch 702 together with the lever actuator 713 substantially corresponds to the friction clutch 202 with the lever actuator 213 of FIG. 3
- the friction clutch 703 with the lever actuator 714 substantially corresponds to the friction clutch 3 with the lever actuator 14 of FIG.
- FIG. 9 shows the dual clutch 801 similar to the dual clutches 1, 201 of FIGS. 1 and 3, with the difference that the friction clutch 802 is open in the force-free state and the friction clutch 803 is a self-retaining friction clutch.
- the friction clutch 802 together with the lever actuator 813 essentially corresponds to the friction clutch 2 with the lever actuator 13 of FIG. 1 and the friction clutch 803 with the lever actuator 814 substantially corresponds to the friction clutch 203 with the lever actuator 214 of FIG. LIST OF REFERENCES
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201080030484.4A CN102575726B (zh) | 2009-07-06 | 2010-06-29 | 双离合器 |
DE112010002868T DE112010002868A5 (de) | 2009-07-06 | 2010-06-29 | Doppelkupplung |
US13/344,968 US8381889B2 (en) | 2009-07-06 | 2012-01-06 | Dual clutch |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009031798 | 2009-07-06 | ||
DE102009031798.8 | 2009-07-06 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/344,968 Continuation US8381889B2 (en) | 2009-07-06 | 2012-01-06 | Dual clutch |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011003386A1 true WO2011003386A1 (de) | 2011-01-13 |
Family
ID=43014252
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2010/000743 WO2011003386A1 (de) | 2009-07-06 | 2010-06-29 | Doppelkupplung |
Country Status (4)
Country | Link |
---|---|
US (1) | US8381889B2 (de) |
CN (1) | CN102575726B (de) |
DE (2) | DE102010025408A1 (de) |
WO (1) | WO2011003386A1 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103453036A (zh) * | 2012-06-04 | 2013-12-18 | Valeo离合器公司 | 三盘式双离合机构 |
TWI483423B (zh) * | 2011-12-29 | 2015-05-01 | Ind Tech Res Inst | 氮化物半導體發光元件 |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101619530B1 (ko) * | 2010-05-17 | 2016-05-11 | 현대자동차주식회사 | 클러치 변속장치 |
DE102011017055A1 (de) * | 2011-04-04 | 2012-10-04 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Kupplungsanordnung für einen KFZ-Antriebsstrang |
DE102012206306A1 (de) | 2011-05-05 | 2012-11-08 | Schaeffler Technologies AG & Co. KG | Betätigungsvorrichtung für eine Doppelkupplung |
DE102012207237A1 (de) | 2011-05-23 | 2012-11-29 | Schaeffler Technologies AG & Co. KG | Betätigungseinrichtung für eine Doppelkupplung |
DE102013201660A1 (de) | 2012-02-22 | 2013-08-22 | Schaeffler Technologies AG & Co. KG | Kupplungssystem |
US9726230B2 (en) * | 2012-07-03 | 2017-08-08 | Schaeffler Technologies AG & Co. KG | Lever system |
KR101417417B1 (ko) * | 2012-11-20 | 2014-07-08 | 현대자동차주식회사 | 차량용 클러치 액추에이터 |
KR101822204B1 (ko) * | 2012-12-17 | 2018-01-26 | 현대자동차주식회사 | 차량용 클러치 액추에이터 |
DE102014210777A1 (de) * | 2014-01-09 | 2015-07-09 | Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg | Kupplungsbaugruppe für die Kupplungsbetätigung in einem Fahrzeuggetriebe |
CN106233019B (zh) * | 2014-04-23 | 2019-01-01 | 舍弗勒技术股份两合公司 | 具有套叠的杆的双离合器 |
DE102015207184A1 (de) * | 2015-04-21 | 2016-10-27 | Schaeffler Technologies AG & Co. KG | Kupplungseinrichtung |
JP6666604B2 (ja) * | 2015-08-06 | 2020-03-18 | 株式会社エフ・シー・シー | クラッチ駆動ユニットおよび鞍乗り型車両 |
KR101766073B1 (ko) * | 2015-12-03 | 2017-08-07 | 현대자동차주식회사 | 더블 클러치조립체 및 그의 엑츄에이터 보조기구 |
DE102016209425B3 (de) * | 2016-05-31 | 2017-11-09 | Schaeffler Technologies AG & Co. KG | Betätigungsvorrichtung für eine Reibungskupplung und Kupplungssystem mit dieser |
DE102016215149A1 (de) | 2016-08-15 | 2018-02-15 | Schaeffler Technologies AG & Co. KG | Spindeltrieb eines Aktors und Kupplung mit mindestens einem solchen Aktor |
KR20220000196A (ko) * | 2020-06-25 | 2022-01-03 | 현대자동차주식회사 | 자동화 변속기용 클러치 액추에이터의 제어방법 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1455106A1 (de) * | 2003-03-03 | 2004-09-08 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Ausrücksysteme |
DE102006019252A1 (de) | 2006-04-26 | 2007-10-31 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Elektronische Aktorik für Doppelkupplungsgetriebe |
FR2917795A1 (fr) * | 2007-06-20 | 2008-12-26 | Peugeot Citroen Automobiles Sa | Commande d'embrayage assistee par un levier a point d'appui variable. |
EP1524446B1 (de) | 2003-10-17 | 2009-03-25 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Kupplungsaggregat |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102008012865A1 (de) * | 2007-03-22 | 2008-09-25 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Selbstnachstellende Reibungskupplung sowie Doppelkupplung mit einer solchen Reibungskupplung |
DE102008058688A1 (de) * | 2007-12-13 | 2009-06-25 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Ausrückvorrichtung für eine Kupplung |
-
2010
- 2010-06-29 DE DE102010025408A patent/DE102010025408A1/de not_active Withdrawn
- 2010-06-29 DE DE112010002868T patent/DE112010002868A5/de not_active Withdrawn
- 2010-06-29 WO PCT/DE2010/000743 patent/WO2011003386A1/de active Application Filing
- 2010-06-29 CN CN201080030484.4A patent/CN102575726B/zh not_active Expired - Fee Related
-
2012
- 2012-01-06 US US13/344,968 patent/US8381889B2/en not_active Expired - Fee Related
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1455106A1 (de) * | 2003-03-03 | 2004-09-08 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Ausrücksysteme |
DE102004009832A1 (de) | 2003-03-03 | 2004-09-16 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Ausrücksysteme |
EP1524446B1 (de) | 2003-10-17 | 2009-03-25 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Kupplungsaggregat |
DE102006019252A1 (de) | 2006-04-26 | 2007-10-31 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Elektronische Aktorik für Doppelkupplungsgetriebe |
FR2917795A1 (fr) * | 2007-06-20 | 2008-12-26 | Peugeot Citroen Automobiles Sa | Commande d'embrayage assistee par un levier a point d'appui variable. |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
TWI483423B (zh) * | 2011-12-29 | 2015-05-01 | Ind Tech Res Inst | 氮化物半導體發光元件 |
CN103453036A (zh) * | 2012-06-04 | 2013-12-18 | Valeo离合器公司 | 三盘式双离合机构 |
CN103453036B (zh) * | 2012-06-04 | 2017-04-12 | Valeo离合器公司 | 三盘式双离合机构 |
Also Published As
Publication number | Publication date |
---|---|
DE102010025408A1 (de) | 2011-01-13 |
US8381889B2 (en) | 2013-02-26 |
DE112010002868A5 (de) | 2012-12-06 |
CN102575726B (zh) | 2015-06-03 |
US20120175213A1 (en) | 2012-07-12 |
CN102575726A (zh) | 2012-07-11 |
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