WO2007128259A1 - Hydrodynamischer drehmomentwandler mit kopplungsfedereinrichtung für den kolben - Google Patents
Hydrodynamischer drehmomentwandler mit kopplungsfedereinrichtung für den kolben Download PDFInfo
- Publication number
- WO2007128259A1 WO2007128259A1 PCT/DE2007/000685 DE2007000685W WO2007128259A1 WO 2007128259 A1 WO2007128259 A1 WO 2007128259A1 DE 2007000685 W DE2007000685 W DE 2007000685W WO 2007128259 A1 WO2007128259 A1 WO 2007128259A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- plate
- torque converter
- spring
- piston
- hydrodynamic torque
- 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
- F16H2045/0221—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
Definitions
- the invention relates to a hydrodynamic torque converter with a driving impeller and a driven impeller, which is rotatably mounted in a housing which can be fastened to the output shaft of a drive unit, and with a converter bridging clutch, which has a piston which rotatably by means of a coupling spring means but is movably connected to the housing in the axial direction.
- the piston is coupled to the housing on the drive side by means of preloaded leaf springs.
- the US 6, 712, 186 B1 shows a hydrodynamic torque converter with a piston which is coupled by means of a toothing without bias to the housing.
- the US 6, 688, 441 B1 shows a hydrodynamic torque converter with a piston which is associated with the housing via a leaf spring.
- the object of the invention is to provide a hydrodynamic torque converter according to the preamble of claim 1, which can transmit greater torques than conventional torque converter.
- the object is achieved with a hydrodynamic torque converter with a driving impeller and a driven turbine wheel, which is rotatably arranged in a housing, which can be fastened to the output shaft of a drive unit, and with a converter bridging clutch, which has a piston, which by means of a coupling spring device rotatably, but movably connected in the axial direction to the housing, achieved by the fact that the piston is the transducer side radially outwardly connected by the coupling spring means under axial bias to the housing. Because the connection takes place radially on the outside of the housing, radial installation space can be saved in the area of a friction surface of the converter lockup clutch, whereby the friction surface and the effective radius of the friction surface can advantageously be increased.
- the transmissible torque depends on the permissible surface pressure and the effective friction lining surface
- larger torques can be transmitted by increasing the effective radius and the friction surface.
- the converter can be designed, for example, for an engine torque of up to 400 Newton meters. This is advantageous, in particular, due to the radial widening of the friction lining. possible. It is advantageous that this extension causes no enlargement of the housing dimensions of the hydrodynamic torque converter. Due to the fact that the piston is connected to the housing radially outward with the housing, for example, the effective radius of the friction lining can be increased by 10 to 12 mm, whereby the friction lining surface can increase by approximately 10%.
- a preferred embodiment of the hydrodynamic torque converter is characterized in that the coupling spring device is arranged between the piston and a converter-side cover of the housing, wherein the piston has a first plate edge with a first toothing and the converter-side cover has a second plate edge with a second toothing.
- the rotationally fixed coupling of the piston to the housing can take place via the toothings and the coupling spring device.
- a further preferred embodiment of the hydrodynamic torque converter is characterized in that the coupling spring means comprises a driver spring ring with V-shaped oppositely disposed spring elements, wherein the spring elements engage in the first and second toothing.
- the Mit supportivefederring the coupling spring means may be formed of a suitable resilient material, for example of a material with the short name Ck75.
- the Mit supportivefederring can fulfill the task of a driver.
- the driver spring ring complementary to the first and second teeth have teeth which are engaged with these and ensure the coupling or the entrainment of the piston.
- the piston has the same speed as the housing of the hydrodynamic torque converter.
- the Mitauerfederring can be designed resiliently and strike against the corresponding plate edges of the piston and the transducer-side cover.
- the axial preload of the piston can be applied against the friction lining of the converter bridging clutch.
- the mode of operation is comparable to two adjoining disc springs. It is also advantageous that the requirement entrainment and axial contact pressure of the piston is ensured by a component, namely the driver or the Mit supportivefederring.
- a further preferred embodiment of the hydrodynamic torque converter is characterized in that the coupling spring means comprises a plate spring ring.
- the coupling spring device has a drive-side disc spring which engages in the first toothing, and a converter-side disc spring which engages in the second toothing, wherein the disc springs are coupled to one another in a rotationally fixed manner.
- the entrainment and the bias so carried over two disc springs the assignment of the individual disc springs to the housing or to the piston is analog.
- the two easily manufactured disc springs for example, also by suitable gears rotatably coupled to each other.
- a further preferred embodiment of the hydrodynamic torque converter is characterized in that the coupling spring device comprises a leaf spring.
- the leaf spring can be arranged directly between the piston and the output-side cover of the housing, so that also the radial space can be saved.
- the assignment of the leaf spring can be done by conventional joining techniques, for example by riveting. It is conceivable that the coupling spring device has a plurality of such leaf springs.
- a further preferred embodiment of the hydrodynamic torque converter is characterized in that the leaf spring is associated with a plate-shaped driver and the piston.
- the plate-shaped carrier can be coupled in a known manner with the housing, for example with the transducer-side cover of the housing, for example via the second toothing.
- the leaf spring can be assigned to the piston and the plate-shaped driver in a known manner, for example by riveting.
- a further preferred embodiment of the hydrodynamic torque converter is characterized in that the disc spring ring engages in the first and in the second toothing. By engaging in the teeth of the piston can be maintained at the rotational speed of the housing. In order to be able to engage in the first and second teeth, the plate spring ring corresponding to the teeth form-fitting adapted teeth.
- the hydrodynamic torque converter is characterized in that the plate spring ring rotatably via a plate carrier the Housing is assigned.
- the disk carrier may be associated with the housing, for example the drive-side cover of the housing, in a known manner.
- the plate carrier may have recesses into which the teeth of the plate spring ring can engage to transmit a torque.
- the plate carrier can engage in a corresponding toothing of the piston, in order to couple this rotation with the housing.
- a further preferred embodiment of the hydrodynamic torque converter is characterized in that the plate spring ring can be inserted in a form-fitting manner in the plate carrier.
- the plate spring ring can be inserted under bias analogous to a bayonet lock in the plate carrier. As soon as the plate spring ring relaxes again, it can thus be held in a form-fitting manner by the plate carrier.
- a torque transmitting device with a arranged in the drive train of a motor vehicle for torque transmission between a drive unit and a transmission hydrodynamic torque converter, as described above.
- Figure 1 is a longitudinal section of a conventional torque transmitting device
- FIG. 2 shows a longitudinal section of a torque transmission device according to the invention with a driver spring ring
- Figure 3 is a three-dimensional exploded view obliquely from the front of the torque transmission device of Figure 2;
- Figure 4 is a detail view of a longitudinal section of an embodiment of the torque transmitting device with a drive-side plate spring and a converter-side plate spring
- Figure 5 is a detail view of another embodiment of a torque transmitting device with a plate spring ring
- Figure 6 is a detail view of a longitudinal section of another embodiment of a torque transmitting device with a connected to a plate-shaped driver leaf spring;
- FIG. 7 shows a detailed view of a further sectional representation of the plate-shaped driver and the leaf spring of the torque transmission device according to FIG. 6;
- FIG. 8 shows a detailed view of a longitudinal section of another torque transmission device with a leaf spring
- Figure 9 is a detail view of another sectional view of the leaf spring of the torque transmission device according to Figure 8.
- Figure 10 is a plan view of a longitudinal section of another torque transmitting device with a plate spring ring and a plate carrier and
- Figures 11 and 12 each show a partially illustrated plan view in the direction of arrow A of Figure 10 on the plate spring ring and the piston of the torque transmission device according to Figure 10, before and after the assembly of the plate spring ring.
- FIG. 1 shows a part of a drive train 1 of a motor vehicle.
- a drive unit 3 in particular an internal combustion engine, from which a crankshaft originates, and a transmission 5, a hydrodynamic torque converter 6 is arranged.
- the crankshaft of the engine 3 is rotatably connected to a housing 10 of the torque converter 6, for example via a drive plate, which is also referred to as a flex plate.
- the housing 10 of the torque converter 6 is rotatable about an axis of rotation 12 and equipped with a housing wall 14 close to the drive and a housing wall 15 remote from the drive.
- a starter ring gear 17 is attached on the drive-near housing wall 14, by means of a radially outwardly extending connecting plate member 16.
- the drive-distant housing wall 15 is combined into a structural unit with a pump 20 of the hydrodynamic torque converter 6.
- a turbine wheel 21 is arranged, which is fastened by means of rivet connection elements to a turbine hub 22.
- the turbine hub 22 is rotatably arranged to an output shaft or input shaft 23 of the transmission 5.
- a stator 24 is arranged in a known manner.
- a converter bridging clutch 26 with a torsional vibration damper 27 is likewise arranged in a known manner.
- the converter bridging clutch 26 comprises a piston 28, which is mounted so as to be rotatable and axially displaceable radially on the outside of the turbine wheel hub 22.
- the piston 28 has radially outside a friction surface, which faces the internal combustion engine 3 and is arranged opposite a further friction surface which is provided on the side facing away from the engine 3 side of the drive housing wall 14. Between the two friction surfaces, a friction plate 29 is arranged, which is rotatably connected to a drive plate 30.
- the drive plate 30 is coupled in a known manner with the interposition of energy storage elements 33, in particular of bow springs, with a damper flange 35 of the torsional vibration damper 27.
- the damper flange 35 is integrally connected to a damper hub 38 by means of a welded connection 36.
- the damper hub 38 in turn is radially inwardly rotatably connected to one end of the input shaft 23 of the transmission 5.
- the piston 28 is coupled to a leaf spring 41.
- the coupling takes place in a required radial space or coupling region between the friction plate 29 of the lockup clutch 26 and the housing wall 14.
- the leaf spring 41 is associated with the housing 10 of the torque converter 6. The effective friction surface of the friction plate 29 is thus arranged radially within the leaf spring 41 and the coupling region of the leaf spring 41 with the piston 28.
- FIG. 2 shows a longitudinal section of a torque converter 6 according to the invention with a coupling spring device 43.
- the differences to the known torque converter 6 according to FIG. 1 are explained below, wherein identical, similar and / or functionally identical components are provided with the same reference numerals.
- the piston 28 is transducer side radially externally connected by the coupling spring means 43 under axial bias to the housing 10.
- the housing 10 has a drive-side cover 45 and a converter-side cover 47.
- the piston 28 is substantially plate-shaped and has a plate rim 49.
- the first plate edge 49 of the piston 28 has a first toothing 51.
- the converter-side cover 47 of the torque converter 6 is likewise substantially plate-shaped and has a second plate rim 53 with a second toothing 55.
- the coupling spring device 43 engages positively in the first toothing 51 of the first plate edge 49 and in the second toothing 55 of the second plate edge 53.
- the piston 28 is rotatably coupled to the housing 10 of the torque converter.
- the piston 28 is connected on the converter side radially outward by the coupling spring means 43 under axial prestress with the housing 10.
- the friction plate 29 advantageously protrudes into the radial installation space still required for the coupling, as shown in FIG. 1, and is therefore extended almost to the housing wall 14, which advantageously results in a greater effective radius of the converter lockup clutch 26.
- the friction linings or friction surfaces of the converter lockup clutch 26 are arranged adjacent to the radially outer housing wall 14. This is possible since the coupling spring device 43 is arranged within the converter-side installation space between the piston 28 and the turbine wheel 21.
- Figure 3 shows a three-dimensional view obliquely from the front in an exploded view of the torque converter 6 shown in Figure 2.
- the coupling spring means 43 has a driver spring ring 57.
- the Mit Conversefederring 57 has V-shaped opposite spring elements 59.
- the spring elements 59 can abut in the assembled state to stops 61 of the corresponding first and second teeth 51, 55 and are brought under pretension.
- An arrow 63 indicates that the spring elements 59 of the driver spring ring 57 hold the piston 28 under tension via the stops 61, which acts on a friction surface 65 of the drive-side cover 45.
- FIG. 4 shows a longitudinal section of a detail of a torque converter 6 with a further coupling spring device 43 which has a drive-side disk spring 67 and a converter-side disk spring 69.
- the drive-side plate spring 67 engages in the first toothing 51 of the first plate edge 49 a.
- the converter-side plate spring 69 engages in the second teeth 55 of the second plate edge 53 of the converter-side cover 47 a.
- the plate springs 67 and 69 also each have a toothing 71, via which the disc springs 67 and 69 mutually rotatably coupled to each other. The torque flow thus takes place, starting from the second plate rim 53, via the toothings 55, 71, 51, finally onto the first plate edge 49 of the piston 28.
- FIG. 5 shows a detailed view of a further torque converter 6 with a disk spring ring 73.
- the disk spring ring 73 has an annular spring leaf 75.
- the spring leaf 75 of the diaphragm spring ring 73 has bent over regions 77, which realize a toothing 79.
- the teeth 79 engage in the first toothing 51 of the first plate edge 49 of the piston 28 a.
- the spring leaf 75 has a toothing 81 which engages in the second toothing 55 of the transducer-side cover 47.
- the rotationally fixed coupling and the bias of the piston 28 take place.
- FIG. 6 shows a further longitudinal section of a detailed view of a torque converter 6 with a leaf spring 83 and a plate-shaped carrier 85.
- the plate-shaped carrier 85 engages in the second toothing 55 of the converter-side cover of the housing 10.
- the driver 85 is rotatably associated with the leaf spring, wherein the assignment is via a rivet 87.
- the leaf spring 83 is associated with the piston 28 under bias.
- Figure 7 shows a partially broken view, seen in alignment of Figure 6, from above, with a partial eruption and a partial section of the driver 85, the leaf spring 83 and the piston 28. Through the outbreak through the rivet 87 is visible. The assignment of the leaf spring 83 to the piston 28 also takes place via a riveting 89. The arrow 63 indicates the direction of force of the leaf spring 83 for biasing the piston 28 at.
- Figure 8 shows a further sectional view of a detail of a torque converter 6 with a leaf spring 83.
- the leaf spring 83 has a bent fixing plate 91.
- the fixing plate 91 and the rivet 87 the leaf spring 83 can be assigned directly to the drive-side cover 45.
- Figure 9 shows a sectional view of the leaf spring 83, seen in alignment of Figure 8, from below on the fixing plate 91, wherein the cutting plane passes through the riveting 89 of the leaf spring 83 with the piston 28.
- the drive-side cover 45 and the rivets 87 are not shown.
- the fixing plate 91 has two bores 93, in which two of the rivets 87 can be introduced.
- FIGS. 11 and 12 show a top view of the plate spring ring 95 and the plate carrier 97 in the direction of an arrow A from FIG. 10.
- FIG. 12 shows the disk spring ring 95 after a partial rotational movement, which is indicated by an arrow 99.
- the plate spring ring 95 analogous to the operation of a bayonet lock, can be positively held within a recess 101 of the disk carrier.
- the plate spring ring To carry out the rotation, as indicated by the arrow 99, the plate spring ring must first be biased into the image plane of FIGS. 11 and 12 so that teeth 103 of a toothing 105 of the plate spring ring 95 can pass through the recess 101 of the plate carrier 97.
- the recess 101 is formed by opposing recesses 107 of the plate carrier 97.
- a toothing of the disk carrier 97 is realized by the recesses 107.
- the toothing 109 of the disk carrier 97 serves on the one hand for fixing the cup spring ring 95 in a bayonet-type manner, as already described, and on the other hand for non-rotatably coupling the piston 28 to the drive-side cover 45 of the housing 10.
- the disk carrier 97 is rotationally fixed to the drive side, for example by means of a weld 111 Lid 45 assigned.
- the toothing 109 of the disk carrier 97 also engages in a toothing 113 of the piston 28 a.
- the piston 28 can be inserted into the drive-side cover 45. Thereafter, the plate spring ring 95, as described above, similar to a bayonet closure can be mounted so that it engages in the plate carrier 97. The plate spring ring can be supported on the plate carrier 97 to produce the required bias and is simultaneously secured against rotation. The direction of the biasing force acting through the piston 28 corresponds to the viewing direction, as indicated by the arrow A. LIST OF REFERENCE NUMERALS
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112007001042.8T DE112007001042B4 (de) | 2006-05-04 | 2007-04-19 | Hydrodynamischer Drehmomentwandler mit Kopplungsfedereinrichtung für den Kolben |
US12/290,756 US20090078522A1 (en) | 2006-04-05 | 2008-11-03 | Hydrodynamic torque converter with coupling spring device for the piston |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006020743 | 2006-05-04 | ||
DE102006020743.2 | 2006-05-04 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/290,756 Continuation US20090078522A1 (en) | 2006-04-05 | 2008-11-03 | Hydrodynamic torque converter with coupling spring device for the piston |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2007128259A1 true WO2007128259A1 (de) | 2007-11-15 |
Family
ID=38325285
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2007/000685 WO2007128259A1 (de) | 2006-04-05 | 2007-04-19 | Hydrodynamischer drehmomentwandler mit kopplungsfedereinrichtung für den kolben |
Country Status (3)
Country | Link |
---|---|
US (1) | US20090078522A1 (de) |
DE (1) | DE112007001042B4 (de) |
WO (1) | WO2007128259A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010049540A1 (de) | 2010-10-25 | 2012-04-26 | Rainer Scholz | Drehmomentwandler |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101341355A (zh) * | 2005-12-20 | 2009-01-07 | 卢克摩擦片和离合器两合公司 | 安置在变矩器的外边缘上的偶合器以及用于将偶合器安装在变矩器中的方法 |
DE102008060577A1 (de) * | 2007-12-12 | 2009-06-18 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Stützplattenbefestigung mit doppelter Überlappung |
DE102011086452C5 (de) | 2010-12-15 | 2023-03-16 | Schaeffler Technologies AG & Co. KG | Drehmomentübertragungseinrichtung mit Berstschutz |
US9845855B2 (en) * | 2014-10-23 | 2017-12-19 | Valeo Embrayages | Torque converter and hydrokinetic torque coupling device having turbine-piston lockup clutch with lockup resistance member |
KR102556824B1 (ko) | 2015-02-17 | 2023-07-17 | 알리손 트랜스미션, 인크. | 토크 컨버터 로크업 클러치 백킹 플레이트 |
US10119603B2 (en) * | 2016-06-02 | 2018-11-06 | Schaeffler Technologies AG & Co. KG | Torque converter including front cover fluid flow baffles |
US10288157B2 (en) * | 2016-08-24 | 2019-05-14 | Schaeffler Technologies AG & Co. KG | Torque converter including integral front cover fluid flow baffles |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2942043A1 (de) * | 1979-10-17 | 1981-05-07 | Automobiles Peugeot, Paris | Getriebe, insbesondere fuer kraftfahrzeuge |
FR2788320A1 (fr) * | 1999-01-12 | 2000-07-13 | Valeo | Appareil d'accouplement hydrocinetique compact, notamment pour vehicule automobile |
FR2797014A1 (fr) * | 1999-07-27 | 2001-02-02 | Valeo | Appareil d'accouplement hydrocinetique |
DE10004608A1 (de) * | 1999-02-09 | 2001-06-21 | Exedy Corp | Überbrückungskupplung für einen Drehmomentwandler |
-
2007
- 2007-04-19 WO PCT/DE2007/000685 patent/WO2007128259A1/de active Application Filing
- 2007-04-19 DE DE112007001042.8T patent/DE112007001042B4/de not_active Expired - Fee Related
-
2008
- 2008-11-03 US US12/290,756 patent/US20090078522A1/en not_active Abandoned
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2942043A1 (de) * | 1979-10-17 | 1981-05-07 | Automobiles Peugeot, Paris | Getriebe, insbesondere fuer kraftfahrzeuge |
FR2788320A1 (fr) * | 1999-01-12 | 2000-07-13 | Valeo | Appareil d'accouplement hydrocinetique compact, notamment pour vehicule automobile |
DE10004608A1 (de) * | 1999-02-09 | 2001-06-21 | Exedy Corp | Überbrückungskupplung für einen Drehmomentwandler |
FR2797014A1 (fr) * | 1999-07-27 | 2001-02-02 | Valeo | Appareil d'accouplement hydrocinetique |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010049540A1 (de) | 2010-10-25 | 2012-04-26 | Rainer Scholz | Drehmomentwandler |
Also Published As
Publication number | Publication date |
---|---|
DE112007001042A5 (de) | 2009-01-29 |
DE112007001042B4 (de) | 2018-10-18 |
US20090078522A1 (en) | 2009-03-26 |
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