WO2016192726A1 - Einrichtung zur übertragung von drehmoment - Google Patents
Einrichtung zur übertragung von drehmoment Download PDFInfo
- Publication number
- WO2016192726A1 WO2016192726A1 PCT/DE2016/200250 DE2016200250W WO2016192726A1 WO 2016192726 A1 WO2016192726 A1 WO 2016192726A1 DE 2016200250 W DE2016200250 W DE 2016200250W WO 2016192726 A1 WO2016192726 A1 WO 2016192726A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- friction
- torque
- wheel
- turbine wheel
- friction element
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- 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
- F16H2045/0205—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type two chamber system, i.e. without a separated, closed chamber specially adapted for actuating a lock-up clutch
-
- 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
-
- 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
- F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
- F16H2045/0278—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch comprising only two co-acting friction surfaces
-
- 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
- F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
- F16H2045/0294—Single disk type lock-up clutch, i.e. using a single disc engaged between friction members
Definitions
- the invention relates to a device for transmitting torque.
- the invention relates to a hydrodynamic torque converter with an integrated lock-up clutch.
- a hydrodynamic torque converter comprises an impeller and a turbine wheel, which are rotatably mounted about a common axis of rotation. By means of a fluid, the two wheels are hydrodynamically coupled together, so that a torque can be transmitted when the two wheels rotate at different speeds about the axis of rotation.
- a lock-up clutch can be used, which closes at higher speeds and can reduce a speed difference between the impeller and the turbine wheel to zero.
- the lock-up clutch is designed to be integrated with the hydrodynamic torque converter, wherein a first friction element is formed on the impeller and a second on the turbine wheel.
- An axial contact force for pressing the friction elements together may use a fluid which under the influence of centrifugal force builds up a hydraulic pressure in the area of one of the friction elements.
- Friction elements embodied with the impeller or the turbine wheel usually have a small wall thickness and are therefore unfavorable with respect to a fitting together.
- An axial contact pressure between the friction elements can thereby be uneven, which can lead to a local increase in contact pressure.
- the friction elements can be overheated in this area, which can result in increased wear or permanent deformation of one of the friction linings.
- the fluid can be heavily thermally stressed in this area, whereby it can also be damaged.
- the invention has for its object to provide an improved means for transmitting torque that overcomes at least one such as these disadvantages.
- the invention solves this problem by means of a device for transmission torque with the features of the independent claims. Subclaims give preferred embodiments again.
- a device for transmitting torque comprises an impeller and a turbine wheel, which are arranged offset axially on a common axis of rotation, wherein the impeller and the turbine wheel by means of a fluid hydrodynamically coupled to each other.
- a first friction element is attached to the pump wheel in a torque-locking manner, and a second friction element is mounted torque-tight on the turbine wheel, wherein the friction elements are set up to be pressed axially against one another in order to produce a frictional connection.
- one of the friction elements is mounted axially movable on the associated wheel.
- the axially movable friction element can be designed in particular as a lamella.
- the friction element can be dimensioned or executed independently of the wheel assigned to it, so that, for example, a rigidity or a material thickness improved can be selected so that the frictional engagement between the friction element and the other friction element can be made uniform.
- An axial pressure on the friction elements can thereby be distributed on a circumference improved around the axis of rotation.
- the frictional engagement between the friction elements can also be distributed in an improved manner on the said circumference, so that the friction elements can have improved durability.
- the opening and closing behavior of the lock-up clutch formed by the friction members can be improved.
- a friction contact surface between the friction elements can be flat, conical or spherical.
- the axially movable friction element can thus be adapted to a shape of the impeller or the turbine wheel improved.
- the device further comprises an elastic axial pressing element, which is mounted between the axially movable friction element and its associated wheel.
- the pressing element itself is axially elastically deformable.
- the pressing element may have a rotating around the axis of rotation plate having an L-shaped cross-section.
- the axial contact pressure element can, for example, Supporting a circumferential sheet metal, which is firmly connected to the associated wheel.
- the pressing element may be embodied for example as an O-ring. The O-ring may be held in an axial groove of the revolving plate in the radial direction.
- the pressing element is preferably arranged to abut on the axially movable friction element on a line contact rotating about the axis of rotation. This is also referred to as a pressure point, which is preferably designed as a circumferential line contact. The distribution of the axially acting force of the pressing element in the radial direction on the friction element can thereby be improved.
- a plurality of radially offset line contacts circulating around the axis of rotation may also be provided.
- two line contacts with different radii can be provided. It may be beneficial to make the axial height of the line contacts different.
- radially outer line contacts are axially closer to the other friction element as compared to radially further inward.
- the contact pressure of the contact pressure element on the friction element can be even better distributed.
- the axial pressure member is shaped such that the line contact migrates radially outwardly with increasing axial contact force between the friction elements.
- the axial contact pressure element may comprise a rotating around the axis of rotation plate with a radial portion, wherein the radial portion is axially elastic.
- the radial section is shaped such that there is line contact between it and the axially movable friction element. With increasing contact pressure, the radial section is deformed so that the line contact moves radially outward. In particular, the closing of the friction elements comprehensive lock-up clutch can be made more uniform or jerk-free.
- the torque connection between the movable friction element and its associated wheel is made by means of a toothing.
- the Ver- toothing can alternatively be performed radially or axially.
- the axial mobility of the friction element can be ensured at the same time good torque.
- the contact pressure element is mounted torque-tight on the wheel assigned to it and the torque connection between the movable friction element and the wheel passes through the contact pressure element.
- a toothing can thus act between the friction element and the contact pressure, so that the pump or the turbine wheel does not need to be provided with a toothing.
- the design, construction and assembly of the pump or turbine wheel can thereby be unaffected by the design of the lock-up clutch.
- the torque connection between the movable friction element and the wheel can also extend over another element, which is preferably connected in a torque-locking manner to the wheel.
- the contact pressure element can be attached in a torque-locking manner to the wheel assigned to it and be shaped such that it still fulfills a further function on the device.
- This function may include, for example, the reception or support of an elastic element, via which a torque can be introduced or removed.
- the elastic element may in particular comprise a cylindrical spring or a bow spring.
- a friction lining is provided on at least one of the friction elements.
- the friction or wear behavior of the friction element can be improved.
- the device is adapted to run in a liquid bath.
- the fluid may comprise a fluid which may also be used for the hydrodynamic coupling of the impeller with the turbine wheel.
- Fig. A hydrodynamic torque converter
- FIG. 1 illustrates exemplary embodiments of an integrated axial lock-up clutch on the torque converter of FIG. 1.
- FIG. 1 shows a hydrodynamic torque converter 100.
- a half section through the torque converter 100 and FIG. 1B is a detail of the torque converter 100 from FIG.
- the torque converter 100 has an axis of rotation 105 about which an impeller 1 10 and a turbine wheel 1 15 are rotatably arranged axially offset.
- the impeller 1 10 and the turbine wheel 1 15 are collectively referred to as wheels 1 10, 1 15.
- a fluid 120 may be introduced to effect a hydrodynamic coupling of the wheels 1 10, 1 15.
- further elements may be provided, which are shown purely by way of example in FIG. 1A, but will not be discussed further here.
- a lock-up clutch 125 is formed, which is adapted to establish a frictional engagement, in order to reduce a speed difference between the impeller 1 10 and the turbine wheel 15.
- the lock-up clutch 125 preferably acts only when the wheels 1 10, 1 15, and in particular the impeller 1 10, rotate about the axis of rotation 105 at a sufficiently high speed.
- the lock-up clutch 125 is preferably disposed on a radially outer side of a region in which the fluid 120 is exchanged between the impeller 1 10 and the turbine wheel 1 15 for transmitting a torque.
- the lock-up clutch 125 is fluid-tight between a housing 130 which extends radially inwards from the pump wheel 110 and the turbine wheel 15. Fluid 120 may accumulate in this space at higher speeds, which then applies hydraulic pressure to lock-up clutch 125 to close it.
- the lock-up clutch 125 comprises a first friction element 135, which is associated with the impeller 1 10 and connected to this torque-locking, and a second friction element 140, which is assigned to the turbine wheel 1 15 and connected to this torque-locking.
- the first friction element 135 is integrated with the impeller 1 10 executed.
- the first friction element 135 may be integrated.
- the second friction element 140 is designed separately and in the illustrated embodiment by means of a toothing 145 torque-coupled to the turbine wheel 1 15.
- a friction lining 150 is provided on one of the friction elements 135, 140.
- An axial pressing member 155 is configured to press the second friction member 140 axially against the first friction member 135.
- a friction contact surface 160 between the friction elements 135 and 140 may be flat, conical or spherical in different embodiments.
- the friction contact surface 160 is planar and extends in a rotation plane about the rotation axis 105. In the radial direction, the friction contact surface 160 between an inner radius 165 and an outer radius 170 is limited.
- a pressure point 175 between the pressing element 155 and the second friction element 140 is preferably located on a radius 180 which lies between the radii 165 and 170 of the friction contact surface 160. It is further preferred that the contact point 175 is circular on a circumference about the axis of rotation 105, so that there is a circumferential line contact.
- the pressing element 155 is supported in the axial direction with respect to the turbine wheel 15, for which purpose a welded connection has been selected by way of example in the present embodiment.
- the elastic contact pressure of the pressing element 155 is realized here by an axial elastic deformability of the pressing element 155.
- the pressing member 155 may comprise an O-ring held in a groove formed on a holding member, which in one embodiment is substantially the shape of the pressing member 155 shown in FIG. 1B.
- the basic operation of the lock-up clutch 125 of FIG. 1 can be varied in a variety of ways.
- the first friction element 135 can be made axially movable. Further variations will be briefly explained with reference to the following figures 2 to 10. It should be noted that the individual features presented in principle with each other and with other embodiments above can be combined.
- FIG. 2 essentially corresponds to that of FIG. 1B.
- the enlarged representation and the omission of a few reference symbols make it easier to recognize details.
- the frictional contact surface 160 is inclined in cross section with respect to the rotation axis 105, so that it assumes the shape of a truncated cone as a whole.
- the toothing 145 on the second friction element 140 extends in the purely radial direction as in FIG. 2.
- a support element 405 with a similar shape is provided. Axially between the support member 405 and the second friction member 140, the pressing member 155 is provided, which may comprise, for example, a rubber or elastomer product.
- the support element 405 may have a circumferential groove 105 about the axis of rotation for fixing the pressing member 155. In the radial direction, the pressing member 155 extends between the radii 165 and 170 of the friction contact surface 160, as shown in Figure 1 B is shown.
- the pressing member 155 may be made wider, whereby a more homogeneous distribution of the axial pressing force on the second friction member 140 can be effected.
- a fluid tightness between the turbine wheel 1 15 and the second friction member 140 may be improved by the wider pressing member 155.
- two pressure points 175 are provided between the pressing element 155 and the second friction element 140.
- the two Pressure points 175 are offset radially and preferably both fall into the region between the radii 165 and 170.
- the pressure point 175 lying radially further outward can be axially closer to the second friction element 140 than the radially further inward one.
- the illustrated pinch points 175 again form line contacts that rotate around the axis of rotation 105.
- three or more pinch points 175 are possible.
- the pressing member 155 may also be configured so that the pressure point 175 is radially displaced with increasing axial load of the pressing member 155. However, he should stay in the range between the radii 165 and 170.
- torque is transmitted between the turbine wheel 15 and the second friction element 140 via the support element 405.
- the toothing 145 is provided between the second friction element 140 and the support element 405.
- the toothing 145 lies radially outside the friction contact surface 160.
- the torque can also be guided alternatively or additionally by the contact pressure element 155.
- FIG. 7 shows a further embodiment in which the torque is not transmitted directly between the second friction element 140 and the turbine wheel 15.
- the toothing 145 is provided radially inside the friction contact surface 160.
- the pressing member 155 is shaped so that it can perform another function. In the illustrated embodiment, it is used in particular for the radial support and / or torque transmission to an elastic element 805 which acts on a circumference about the axis of rotation 105.
- the elastic member 805 may comprise a cylinder or bow spring and serve for coupling or decoupling a torque.
- Figures 9 and 10 show embodiments in which instead of the second friction element 140, the first friction element 135 is designed to be axially movable.
- the first friction element 135 transmits at least a part of the second friction element 140 introduced torque via an additional connection with the impeller 1 10, for example via the illustrated teeth 145 or even, for example, a caulking, a weld or other connection.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112016002509.2T DE112016002509B4 (de) | 2015-06-05 | 2016-05-25 | Einrichtung zur Übertragung von Drehmoment |
CN201680029995.1A CN107690537B (zh) | 2015-06-05 | 2016-05-25 | 用于传递扭矩的装置 |
US15/579,485 US10571006B2 (en) | 2015-06-05 | 2016-05-25 | Device for transmitting torque |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015210364.1 | 2015-06-05 | ||
DE102015210364.1A DE102015210364A1 (de) | 2015-06-05 | 2015-06-05 | Einrichtung zur Übertragung von Drehmoment |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2016192726A1 true WO2016192726A1 (de) | 2016-12-08 |
Family
ID=56194191
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2016/200250 WO2016192726A1 (de) | 2015-06-05 | 2016-05-25 | Einrichtung zur übertragung von drehmoment |
Country Status (4)
Country | Link |
---|---|
US (1) | US10571006B2 (de) |
CN (1) | CN107690537B (de) |
DE (2) | DE102015210364A1 (de) |
WO (1) | WO2016192726A1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN110822050B (zh) * | 2019-11-26 | 2021-08-31 | 奇瑞汽车股份有限公司 | 动力传递系统 |
US11913530B2 (en) * | 2021-09-02 | 2024-02-27 | Schaeffler Technologies AG & Co. KG | Torque converter with turbine driven clutch connection |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2317556A1 (fr) * | 1975-06-28 | 1977-02-04 | Honda Motor Co Ltd | Convertisseur hydraulique de couple avec un embrayage de blocage entre la pompe et la turbine |
FR2428188A1 (fr) * | 1978-06-06 | 1980-01-04 | Honda Motor Co Ltd | Convertisseur de couple |
DE102014224114A1 (de) * | 2013-12-03 | 2015-06-03 | Schaeffler Technologies AG & Co. KG | Drehmomentwandler mit integrierter Dreischeiben-Überbrückungskupplung |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2943516A (en) * | 1957-07-05 | 1960-07-05 | Gen Motors Corp | Transmission |
EP0125428A1 (de) | 1983-03-23 | 1984-11-21 | ZF FRIEDRICHSHAFEN Aktiengesellschaft | Hydrodynamische Baueinheit mit Überbrückungskupplung |
FR2749633B1 (fr) | 1996-06-10 | 1998-08-28 | Valeo | Appareil d'accouplement hydrocinetique, notamment pour vehicule automobile |
FR2776739B1 (fr) | 1998-03-26 | 2000-06-30 | Mannesmann Sachs Ag | Embrayage de coupure pour un convertisseur hydrodynamique de couple comportant un piston fixe par un element en elastomere |
DE102014217460A1 (de) | 2014-09-02 | 2016-03-03 | Schaeffler Technologies AG & Co. KG | Einrichtung zur Übertragung von Drehmoment |
US9803735B2 (en) * | 2014-12-02 | 2017-10-31 | Schaeffler Technologies AG & Co. KG | Normally engaged turbine clutch |
US9752667B2 (en) * | 2014-12-05 | 2017-09-05 | Valeo Embrayages | Torque converter and hydrokinetic torque coupling device having turbine-piston lockup clutch, and related methods |
US10151376B2 (en) * | 2017-04-07 | 2018-12-11 | Schaeffler Technologies AG & Co. KG | Torque converter including turbine piston and multi-plate clutch assembly |
-
2015
- 2015-06-05 DE DE102015210364.1A patent/DE102015210364A1/de not_active Withdrawn
-
2016
- 2016-05-25 DE DE112016002509.2T patent/DE112016002509B4/de active Active
- 2016-05-25 US US15/579,485 patent/US10571006B2/en active Active
- 2016-05-25 CN CN201680029995.1A patent/CN107690537B/zh active Active
- 2016-05-25 WO PCT/DE2016/200250 patent/WO2016192726A1/de active Application Filing
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2317556A1 (fr) * | 1975-06-28 | 1977-02-04 | Honda Motor Co Ltd | Convertisseur hydraulique de couple avec un embrayage de blocage entre la pompe et la turbine |
FR2428188A1 (fr) * | 1978-06-06 | 1980-01-04 | Honda Motor Co Ltd | Convertisseur de couple |
DE102014224114A1 (de) * | 2013-12-03 | 2015-06-03 | Schaeffler Technologies AG & Co. KG | Drehmomentwandler mit integrierter Dreischeiben-Überbrückungskupplung |
Also Published As
Publication number | Publication date |
---|---|
DE112016002509A5 (de) | 2018-03-08 |
CN107690537A (zh) | 2018-02-13 |
DE112016002509B4 (de) | 2023-03-16 |
US20180149250A1 (en) | 2018-05-31 |
US10571006B2 (en) | 2020-02-25 |
CN107690537B (zh) | 2020-10-27 |
DE102015210364A1 (de) | 2016-12-08 |
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