WO2017025088A1 - Drehmomentübertragungseinrichtung - Google Patents
Drehmomentübertragungseinrichtung Download PDFInfo
- Publication number
- WO2017025088A1 WO2017025088A1 PCT/DE2016/200340 DE2016200340W WO2017025088A1 WO 2017025088 A1 WO2017025088 A1 WO 2017025088A1 DE 2016200340 W DE2016200340 W DE 2016200340W WO 2017025088 A1 WO2017025088 A1 WO 2017025088A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- clutch
- torque
- torque transmission
- speed
- predefined
- 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
- F16D33/00—Rotary fluid couplings or clutches of the hydrokinetic type
-
- 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
- F16D39/00—Combinations of couplings according to two or more of the groups F16D31/00 - F16D37/00
-
- 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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
-
- 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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
-
- 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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0247—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means having a turbine with hydrodynamic damping means
Definitions
- the invention relates to a torque transmission device according to claim 1.
- an improved torque transmitting device may be provided by the torque transmitting device including an input side, a hydrodynamic converter, a clutch device, a flange, and a damper device.
- the damper device comprises a first damper arrangement.
- the converter comprises a turbine wheel.
- the first damper assembly is coupled on the input side with the input side and the output side with the flange torque-locking.
- the coupling device is designed to connect the turbine wheel in a torque-locked manner to the flange in a switchable manner.
- This embodiment has the advantage that the first damper arrangement can be operated in two different operating states, so that a damper behavior can be adapted in a simple manner.
- the coupling device has a first clutch.
- the first clutch is connected between the flange and the turbine wheel. assigns. In the closed state, the first clutch connects the turbine wheel with the flange at least partially torque-locking. In the open state of the first clutch torque transmission via the first clutch between the turbine wheel is interrupted.
- the first clutch is closed below a first predefined rotational speed and at least partially open above the first predefined rotational speed.
- the first clutch has a second predefined speed.
- the second predefined speed is greater than the first predefined speed. Between the first predefined speed and the second predefined speed, the first clutch is partially opened. Above the second predefined speed, the first clutch is fully open. As a result, a sudden switching of the first clutch and thus a sudden switching of the operating states of the torque transmission device can be avoided. Thus, the torque transmission device has a particularly comfortable operating behavior.
- the torque transmission device has an intermediate flange, the damper device comprising a second damper arrangement, wherein the second damper arrangement is connected on the input side to the input side and output side to the intermediate flange, wherein the first damper arrangement is connected on the input side to the intermediate flange.
- the torque transmission device has an intermediate flange.
- the intermediate flange is disposed between the first damper assembly and the second damper assembly.
- the coupling device has a second coupling.
- the second clutch is disposed between the turbine wheel and the intermediate flange. When closed, the second clutch connects the turbine wheel with the intermediate flange at least partially. ment conclusive. In the opened state of the second clutch torque transmission via the second clutch between the turbine wheel and the intermediate flange is interrupted.
- a driving self-shape of a drive motor which is couplable to the input side and a damper shape of a centrifugal pendulum which is couplable to the flange can be kept spaced from each other, so that the two eigenmodes do not influence each other.
- an insulation of the torque transmission device can be designed particularly efficiently. It is also avoided that occur in the operation of the torque transmission device in the speed band amplitudes in the Tilgerform that can not be easily passed through.
- the second clutch is opened below a third predefined speed and closed above the third predefined speed.
- the first speed and the third speed are identical or different.
- the fourth clutch has a fourth predefined speed.
- the fourth speed is greater than the third predefined speed. Between the third predefined speed and the fourth predefined speed, the second clutch is partially closed. Above the fourth predefined speed, the second clutch is fully closed.
- the fourth predefined rotational speed preferably corresponds essentially to the second predefined rotational speed.
- the first and / or second damper arrangement has at least one spring element.
- the spring element is designed as a bow spring or compression spring.
- the clutch device in particular the first clutch and / or the second clutch, centrifugally and / or electrically and / or hydraulically and / or pneumatically and / or mechanically operated.
- Figure 1 is a schematic representation of a Drehmomentübertragungseinrich- device according to a first embodiment
- Figure 2 is a graph of a speed variation plotted against a speed
- FIG. 3 shows a diagram of a maximum torque transmittable by means of a clutch of the torque transmission device shown in FIG. 1, plotted against the rotational speed;
- Figure 4 is a schematic representation of a torque transmitting device according to a second embodiment
- FIG. 5 shows a section of the torque transmission device shown in FIG. 4;
- FIG. 6 shows a diagram of a maximum torque transmittable across the rotational speed by means of the clutches of the torque transmission device shown in FIGS. 4 and 5;
- FIG. 7 shows a diagram of a speed fluctuation plotted against the rotational speed of the torque transmission device shown in FIGS. 4 and 5.
- FIG. 1 shows a schematic illustration of a torque transmission device 10 according to a first embodiment.
- the torque transmission device 10 may be part of a drive train of a motor vehicle.
- FIG. masses represented by rectangular boxes.
- Substantially stiff torque transmissions are shown with straight lines.
- a soft torque transmission is shown with a jagged line.
- the torque transmission device 10 has an input side 15 and an output side 20.
- the input side 15 is torque-connected to a drive motor 25.
- the drive motor 25 may be designed as a reciprocating engine, in particular as an internal combustion engine.
- the drive motor 25 has a drive motor form.
- the output side 20 is connected torque-locked with a translation device 30.
- the translation device 30 may in this case be designed as a spur gear and / or planetary gear or otherwise.
- the translation device 30 may be connected torque-tight on the output side with other components of the drive train.
- the translation device 30 has an inertia J G.
- the torque transmission device 10 comprises a lockup clutch 35, a hydrodynamic converter 40, a clutch device 50, a centrifugal force pendulum 51 and a flange 52.
- the converter 40 comprises a pump wheel 55 with an inertia J P. Furthermore, the converter 40 comprises a turbine wheel 60 with an inertia J T.
- the impeller 55 is torque-connected to the input side 15.
- the input side 20 is torsionally connected by means of an output shaft 56 of the drive motor 25 to the drive motor 25 in the converter 40, the impeller 55 is coupled by means of hydrodynamic effects torque-locking with the turbine wheel 60.
- the lockup clutch 35 has a lockup clutch input side 65 and a lockup clutch output side 70.
- the lockup clutch 35 is switchable. In the closed state, the lock-up clutch 35 connects the lock-up clutch input side 65 with the lock-up clutch output side 70 in a torque-locking manner. In the open state, the lock-up clutch input side 65 is disconnected from the lock-up clutch output side 70. The lock-up clutch input side 65 is connected to the pump gear 55.
- the damper device 45 includes a first damper assembly 71.
- the first damper assembly 71 is the input side connected to the lock-up clutch output side 70 torque.
- the first damper arrangement 71 has at least one first spring element 75.
- the first spring element 75 may be, for example, a compression spring. Also, the first spring element 75 may be formed differently. For example, the first spring element 75 can also be a bow spring
- the flange 52 is preferably designed as a hub flange and has an inertia J N F.
- the flange 52 preferably forms the output side 20 of the torque transmission device 10.
- the flange 52 is connected via a transmission input shaft 80 torque-locking with the translation device 30 connected.
- the transmission input shaft 80 is preferably soft, so that in Figure 1, the transmission input shaft 80 is shown with a jagged line. Also, the transmission input shaft 80 may be rigid.
- the first damper assembly 71 is coupled on the output side with the flange 52
- the centrifugal pendulum 51 is preferably arranged on the turbine wheel 60. Also, the centrifugal pendulum 51 may be disposed at another position of the torque transmitting device 10. The centrifugal pendulum 51 has a centrifugal pendulum shape.
- the coupling device 50 comprises a first coupling 81.
- the first clutch 81 has a first clutch input side 85 and a first clutch output side 90 on.
- the first clutch 81 is arranged between the flange 52 and the turbine wheel 60, wherein the first clutch input side 85 with the turbine wheel 60 and the first coupling output side 90 to the flange 52 are torque-coupled.
- the first clutch 81 In the open state, the first clutch 81 separates a torque transmission via the first clutch 81 between the turbine wheel 60 and the flange 52.
- the first clutch 81 connects the turbine wheel 60 with the flange 52 at least partially torque-locking.
- the first clutch 81 may be looped or completely closed.
- the first clutch 81 may be centrifugally operated and / or electrically operated and / or hydraulically actuated and / or pneumatically actuated and / or mechanically actuated. Also, the first clutch 81 may include an unillustrated actuator connected to a controller. By means of the actuator, the controller can open and close the first clutch 81. Constructively, the first clutch 81 can be configured hydrodynamically and / or with friction partners, which produce a frictional connection for the torque-locking connection of the first clutch input side 85 to the first clutch output side 90.
- the torque transmission device 10 essentially has three operating states. In a first operating state, the lockup clutch 35 is opened. Thus, torque transmission between the lock-up clutch input side 65 and the lockup clutch output side 70 is interrupted.
- the drive motor 25 provides torque.
- the torque is introduced via the input side 15 in the torque transmission device 10.
- the torque is transmitted via the converter 40 to the first clutch input side 85.
- the first clutch 81 is closed, otherwise via the torque transmission means 10 no torque between the input side 15 and the output side 20 is transferable.
- the torque is transmitted to the output side 20 via the first clutch 81. From the output side 20, the torque is transmitted to the translation device 30 via the transmission input shaft 80. Due to the arrangement of the centrifugal pendulum pendulum 51 on the turbine wheel 60, the centrifugal pendulum 51 eliminates torsional vibrations in the torque output side of the converter 40th
- the lockup clutch 35 is closed.
- the drive motor 25 provides the torque.
- the torque is introduced via the input side 1 5.
- the lockup clutch 35 transmits the torque to its lockup clutch output side 70.
- the torque is further input to the damper device 45.
- the damper device 45 reduces torsional vibrations present in the torque, so that a smoother torque is provided on the output side of the damper device 45.
- the torque is transmitted via the damper device 45 to the output side 20.
- the first damper arrangement 71 has a first operating behavior with a first eigenform.
- the first clutch 81 is opened, so that the turbine wheel 60 is decoupled from the flange 52.
- the torque is passed via the transmission input shaft 80 on to the translation device 30 on.
- a third operating state which substantially corresponds to the second operating state
- the first clutch 81 is closed.
- the turbine wheel 60 is torque-coupled to the flange 52.
- the moment of inertia J T , JNF of the turbine wheel 60 and the flange 52 add up.
- This causes the first damper assembly 71 to have a second performance that is different than the first performance.
- the second operating behavior of the torque transmission device 10 is compared to the first changed operating state characterized in that the centrifugal pendulum 51 is engaged via the first clutch 81 with.
- FIG. 2 shows a diagram of a rotational speed fluctuation ⁇ on the output side 20 plotted against the rotational speed n.
- the diagram has a first graph 100 and a second graph 105.
- the first graph 100 corresponds to the first operating behavior of the torque transmission device 10 in the second operating state described in FIG.
- the second graph 105 corresponds to the third operating state of the torque transmitting device 10 described in FIG. 1.
- the first graph 100 differs from the second graph 105 in that, as the rotational speed n decreases, the rotational speed fluctuation ⁇ increases earlier than in the second graph 105.
- the first clutch 81 is controlled speed-dependent.
- the first clutch 81 is closed below a first predefined rotational speed n G i and the torque transmission device is operated in the third operating state.
- the first clutch 81 is at least partially opened and the torque transmission device 10 operates in the second operating state.
- the second operating state differs from the third operating state in that the uncoupling of the turbine wheel 60 from the flange 52 makes it impossible for the centrifugal-force pendulum form to have any further influence on the torque-transmitting device 10.
- the torque transmitting device can be operated in each case in their favorable operating state, when the torque transmission device 10 has a lower speed fluctuation.
- the positive properties of the first damper arrangement 71 can be used as a function of rotational speed, so that the torque transmission device 10 has an overall improved operating behavior.
- a negative behavior eg. B. a rocking of speed fluctuations above the first predefined speed n G i in the third operating state of the torque transmission device 10, that is, when the first clutch 81 is closed, be avoided.
- FIG. 3 shows a diagram of a switching state of the first clutch 81 of the clutch device 50 in a variant of the first clutch 81.
- a torque MRI which is transmittable maximally with the first clutch 81 above the rotational speed n is plotted.
- the first clutch 81 has a second predefined rotational speed n G 2 in relation to the first clutch 81 shown in FIGS. 1 and 2.
- the first clutch 81 between the first predefined speed n G i and the second predefined speed n G 2 is partially opened. In this state, therefore, the first clutch 81 can be operated by slipping. Above the second predefined speed n G2 , the first clutch 81 is fully opened. This configuration of the first clutch 81 causes no jerky switching of the first clutch 81 results in a jerky change in the behavior of the torque transmission device 10.
- FIG. 4 shows a schematic illustration of a torque transmission device 10 according to a second embodiment.
- the torque transmission device 10 is designed similarly to the torque transmission device 10 shown in FIG. Deviating from this, the coupling device 50 has, in addition to the first clutch 81 and a second clutch 200.
- the second clutch 200 may be identical to the first clutch 81. Also, the second clutch 200 may be formed differently from the first clutch 81. Also, the second clutch 200 may be actuated via the first clutch 81 or may have an operation deviating from the first clutch 81.
- the second clutch 200 may be closed below a predefined third rotational speed n G3 and opened above the predefined third rotational speed n G3 .
- the second clutch 200 has a second clutch input side 205 and a second clutch output side 210.
- the second clutch input side 205 is rotationally rotationally connected to the turbine wheel 60.
- the damper device 45 includes, in addition to the first damper assembly 71, a second damper assembly 215.
- the second damper assembly 215 may be formed identically to the first damper assembly 71. Also, the second damper assembly 215 may be formed differently from the first damper assembly 71.
- the second damper assembly 215 has a second spring element 220. The second spring element 220 is coupled to the flange 52.
- an intermediate flange 225 is provided between the first damper assembly 71 and the second damper assembly 215, an intermediate flange 225 is provided.
- the second damper arrangement 215 is coupled to the intermediate flange 225.
- the second damper assembly 215 is connected to the lock-up clutch output side 70.
- the first damper device 71 is coupled on the input side with the intermediate flange 225 and on the output side with the flange 52.
- the second coupling output side 210 is torque-coupled to the intermediate flange 225.
- the intermediate flange 225 has an inertia J Z F.
- the mass inertia J Z F of the intermediate flange 225 may be different or identical to the mass inertia JNF of the flange 52.
- FIG. 5 shows a detail of the torque transmission device 10 shown in FIG. 3. Only the components of the torque transmission device active in FIG. 4 to the closed lockup clutch are shown.
- the second and third operating states of the torque transmitting device 10 are similar to the operating state described in FIGS. 1 and 2.
- the second clutch 200 is opened, whereas the first clutch 81 is closed.
- damper device 45 acts as a turbine damper (TD), which is particularly soft and can particularly well compensate for high speed variations, especially at lower speeds.
- the switching of the first and second clutches 81, 200 can take place synchronously at the predefined first rotational speed n G i.
- FIG. 6 shows a diagram of the rotational speed fluctuation ⁇ plotted against the rotational speed n as a function of the second and third operating states.
- three graphs 400, 405, 410 are shown in the diagram.
- a first graph 400 corresponds to the second operating state if the torque transmission device 10 were switched in this way only via the rotational speed n.
- a second graph 405 corresponds to the third operating state of the torque transmission device 10 shown in FIG. 4, if the torque transmission device 10 were operated over the entire rotational speed n exclusively in the third operating state.
- a third graph 410 shows the operating behavior of the torque transmission device 10, wherein at the first speed n G i is switched from the second operating state to the third operating state.
- the torque transmission device 10 has a particularly low speed fluctuation ⁇ over the entire rotational speed spectrum. This avoids that the drive own form of the drive motor 25 and the Tilgereigenform the centrifugal pendulum 51 can influence each other. In particular, it is avoided that in the third operating state of the torque transmission device 10, the drive own form is close to the Tilgereigenform of the centrifugal pendulum 51. This avoids that an insulation to the torque transmission device 10 is unacceptable early before the drive own form.
- the drive characteristic is lower than in the third operating state.
- the isolation of the torque transmission device 10 to the first speed n G i is sufficient. Because the
- Tilgereigenform in the mobile range above the first speed n G i (in Figure 6 after the first speed n G i rising mountain of the first graph 400) and often has amplitudes that can not be easily passed through, by switching the clutches 81, 200 to the third operating state, these amplitudes in the rotational speed fluctuation ⁇ of the torque transmission device 10 are avoided.
- the positive characteristics of the torque transmitting device 10, in particular in the second operating state of the present turbine damper (TD) in the low speed range, with the positive properties in the third operating state of the torque transmitting device 10, in particular when the damper device 45 is formed as a double torsional damper (DTD), in the higher Speed range can be combined.
- Figure 7 shows a diagram of a transmittable maximum with the clutch 81, 200 Moments M R i, M R2 in function of the speed n in a variant of the torque transmission device 10 shown in Figures 4 through. 6
- the diagram comprises a first graph 300 and a second graph 305.
- the first graph 300 corresponds to the graph 100 of the first clutch 81 shown in FIG.
- the second graph 305 corresponds to the circuit and the maximum torque M R2 that can be transmitted with the second clutch 200.
- the second clutch 200 is open below a third predefined speed n G 3.
- the third predefined rotational speed n G 3 can be identical to the first rotational speed n G i.
- the third predefined speed n G 3 and the first predefined speed n G i may be different.
- the second clutch 200 is partially closed above the third rotational speed n G3 . As the rotational speed n increases, the second clutch 200 continues to be closed, wherein above a fourth predefined rotational speed n G , which in the embodiment is identical to the second predefined rotational speed n G2 , the second clutch 200 is completely closed.
- a fourth predefined rotational speed n G which in the embodiment is identical to the second predefined rotational speed n G2
- the second clutch 200 is completely closed. If the first clutch 81 and the second clutch 200 are designed identically by way of example, then the maximum torque M R i, M R2 which can be transmitted with the first and the second clutch 81, 200 can be identical. If the clutches 81, 200 are designed differently, it goes without saying that the torques M R i, M R2 which can be transmitted by means of the clutches 81, 200 can be different.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201680047082.2A CN107923452B (zh) | 2015-08-10 | 2016-07-22 | 转矩传递装置 |
DE112016003670.1T DE112016003670A5 (de) | 2015-08-10 | 2016-07-22 | Drehmomentübertragungseinrichtung |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015215199.9A DE102015215199A1 (de) | 2015-08-10 | 2015-08-10 | Drehmomentübertragungseinrichtung |
DE102015215199.9 | 2015-08-10 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2017025088A1 true WO2017025088A1 (de) | 2017-02-16 |
Family
ID=56681912
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2016/200340 WO2017025088A1 (de) | 2015-08-10 | 2016-07-22 | Drehmomentübertragungseinrichtung |
Country Status (3)
Country | Link |
---|---|
CN (1) | CN107923452B (de) |
DE (2) | DE102015215199A1 (de) |
WO (1) | WO2017025088A1 (de) |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2008064638A1 (de) * | 2006-11-29 | 2008-06-05 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Kraftübertragungsvorrichtung, insbesondere multifunktionswandlereinheit |
DE102012205761A1 (de) * | 2011-04-21 | 2012-10-25 | Schaeffler Technologies AG & Co. KG | Drehmomentwandler |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102066797B (zh) * | 2008-06-19 | 2014-05-07 | 舍弗勒技术股份两合公司 | 可转换的离合器装置,及用于交通工具的传动系和其方法 |
WO2010043194A1 (de) * | 2008-10-16 | 2010-04-22 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Hydrodynamischer drehmomentwandler |
JP5527873B2 (ja) * | 2009-03-18 | 2014-06-25 | 株式会社エフ・シー・シー | 動力伝達装置 |
DE202010018604U1 (de) * | 2009-04-27 | 2018-04-27 | Schaeffler Technologies AG & Co. KG | Hydrodynamischer Drehmomentwandler |
JP2012533037A (ja) * | 2009-07-16 | 2012-12-20 | シェフラー テクノロジーズ アクチエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフト | トルク伝達装置 |
DE102011016999A1 (de) * | 2010-04-26 | 2012-03-29 | Schaeffler Technologies Gmbh & Co. Kg | Verfahren zur Adaption eines Tastpunktes einer Kupplung in einem Triebstrang eines Kraftfahrzeuges |
US20150090555A1 (en) * | 2012-05-17 | 2015-04-02 | Toyota Jidosha Kabushiki Kaisha | Power transmission system |
US8608604B1 (en) * | 2012-10-19 | 2013-12-17 | Caterpillar Inc. | Torque divider and torque converter with lockup clutch |
-
2015
- 2015-08-10 DE DE102015215199.9A patent/DE102015215199A1/de not_active Withdrawn
-
2016
- 2016-07-22 WO PCT/DE2016/200340 patent/WO2017025088A1/de active Application Filing
- 2016-07-22 CN CN201680047082.2A patent/CN107923452B/zh not_active Expired - Fee Related
- 2016-07-22 DE DE112016003670.1T patent/DE112016003670A5/de not_active Withdrawn
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2008064638A1 (de) * | 2006-11-29 | 2008-06-05 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Kraftübertragungsvorrichtung, insbesondere multifunktionswandlereinheit |
DE102012205761A1 (de) * | 2011-04-21 | 2012-10-25 | Schaeffler Technologies AG & Co. KG | Drehmomentwandler |
Also Published As
Publication number | Publication date |
---|---|
CN107923452B (zh) | 2019-11-26 |
DE112016003670A5 (de) | 2018-04-26 |
DE102015215199A1 (de) | 2017-02-16 |
CN107923452A (zh) | 2018-04-17 |
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