WO2017028859A1

WO2017028859A1 - Centrifugal pendulum absorber, and hydrodynamic torque converter with centrifugal pendulum absorber

Info

Publication number: WO2017028859A1
Application number: PCT/DE2016/200378
Authority: WO
Inventors: Stephan Maienschein
Original assignee: Schaeffler Technologies AG & Co. KG
Priority date: 2015-08-20
Filing date: 2016-08-15
Publication date: 2017-02-23
Also published as: CN107923480A; DE102015215891A1; CN107923480B; DE112016003780A5

Abstract

The invention relates to a centrifugal pendulum absorber (4) and a hydrodynamic torque converter (1) comprising a housing (14) arranged around the transmission input shaft (6), and an impeller (3) integrated into the housing (14).The housing (14) receives a turbine (10), arranged such that it can rotate with respect to the housing, a torque converter lock-up clutch (9) operatively arranged between the impeller (3), and the turbine (10), and optionally a torsional vibration damper (13) and a centrifugal pendulum absorber (4). In order to render the centrifugal pendulum absorber (4) less noisy and more robust, a stop damping element (50) is provided between the pendulum rollers (29) and the pendulum carrier (30).

Description

Centrifugal pendulum and hydrodynamic torque converter with

centrifugal pendulum

The invention relates to a centrifugal pendulum and equipped with this hydrodynamic torque converter with a arranged around the transmission input shaft housing, an integrated pump in the housing impeller, wherein the housing receives a relation to this rotatably arranged turbine wheel, an effective between the impeller and turbine torque converter lock-up clutch and optionally a torsional vibration damper ,

Centrifugal pendulum are sufficiently known from drive trains of motor vehicles. Here, a support member is rotatably received about an axis of rotation, for example, a crankshaft of an internal combustion engine, a transmission input shaft of a transmission or the like. Pendulum masses distributed over the circumference are arranged on the support part, which are suspended in a plane perpendicular to the axis of rotation with respect to the support part in a pendulum fashion on the support part. As a result of this pendulum suspension, the pendulum masses in the centrifugal force field of the rotating carrier part form a rotational speed adaptive torsional vibration damper in that the pendulum masses withdraw energy from the drive train during torque peaks by means of appropriate deflection and supply it at torque minima.

For example, as known from WO2014 / 082629 A1, pendulum masses can be arranged axially between two side parts, which form the carrier part, distributed over the circumference. Alternatively, as known from DE 10 2012 221 949 A1, pendulum mass parts can be arranged on both sides of the carrier part. Axially opposite ing pendulum mass parts are connected by means of connecting means with each other to pendulum masses, wherein the connecting means pass through recessed corresponding recesses of the support member. A centrifugal pendulum can - as disclosed for example with reference to the above-mentioned publications WO2014 / 082629 A1, DE 10 2012 221 949 A1 - be provided on a one-mass flywheel, for example, a one-mass flywheel made of sheet metal. As is known, for example, from the documents WO2014 / 023303 A1 and DE 10 2013 201 981 A1, one or more centrifugal pendulums on a torsional vibration damper, corresponding to the document WO2014 / 1 14 280 A1 on a clutch disc, according to the document EP 2 600 030 A1 hydrodynamic torque converter, be provided on a housing of a friction clutch or similar locations of the drive train. Furthermore, hydrodynamic torque converter from drive trains of motor vehicles are known and are preferably arranged between an internal combustion engine and a transmission. In this case, the converter function of the torque converter with torque increase is preferably used to start the motor vehicle by the torque from the housing, which is driven by means of the crankshaft of the internal combustion engine, is passed through the impeller. The impeller thereby drives a turbine wheel, which transmits the torque via an output part under support to a stator for torque increase to a transmission input shaft of the transmission. At higher speeds, a lock-up clutch operatively arranged between the impeller and the turbine wheel is closed, so that the torque is reduced while bypassing the converter component. th is transmitted directly from the housing via the output part to the transmission input shaft and thus the deteriorating efficiency of the converter components is eliminated at higher speeds. The internal combustion engines used, for example, 4-cylinder diesel engines, have high rotational irregularities, so that in the housing of the torque converter one or more torsional vibration dampers are provided, depending on their arrangement with open and / or closed torque converter lockup clutch between the housing and the output part or between the turbine wheel and the output part of the torque converter are effective. Here, under a torsional vibration damper in a known manner to understand an arrangement with an input and an output part, which are against the action of a spring device limited against each other rotated. Such torsional vibration dampers may include a plurality of damper stages, which are arranged to each other serially and / or in parallel.

For improved vibration isolation of the torsional vibrations of the internal combustion engine, the use of centrifugal pendulums in the housing of the torque converter is furthermore known, which are effectively integrated in the housing in conjunction with torsional vibration dampers. For example, from WO 2010/043194 A1 discloses a hydrodynamic torque converter with a plurality of effective in the open and closed state of the lockup clutch damper assemblies and a centrifugal pendulum, the centrifugal pendulum is connected directly to the turbine wheel. From DE 198 04 227 A1, a torque converter with a torsional vibration damper assigned to one of the torque converter lock-up clutch is attached. ordered balance masses that roll on pendulum rollerways.

The object of the invention is the development of a centrifugal pendulum and a torque converter with a centrifugal pendulum. In particular, object of the invention to provide a robust and low-wear centrifugal pendulum.

The object is solved by the subject matter of claim 1. The dependent of this or independent claims give advantageous embodiments of the subject matter of claim 1 again. The proposed centrifugal pendulum includes a pendulum roller carrier arranged about a rotation axis and distributed over the circumference arranged on this pendulum rollers. The spherical rollers may be formed, for example, as discs made of sheet metal and round, elliptical, be formed in the form of drops or similar shape. The spherical rollers are captive secured to the pendulum roller carrier. Under centrifugal force of the pendulum roller carrier rotating about the rotation axis, the spherical rollers form a rolling contact by means of a rolling surface with a rolling surface of a pendulum roller conveyor of the pendulum roller carrier. Preferably, the pendulum roller carrier may be formed in two parts or more parts of disc parts such as side panels made of sheet metal, wherein the spherical rollers are accommodated axially between them in individual pendulum spaces separated from each other. Both disc parts are firmly connected to each other, for example, riveted or welded. One or both disc parts are rotationally driven, for example, from a crankshaft or transmission input shaft or in an aggregate, for example, input and / or output side in a clutch disc, a torque converter, a friction clutch, a double clutch, an electric machine or the like integrated Under the action of centrifugal force, spherical rollers shift against the pendulum roller conveyors and shift there for the eradication of torsional vibrations. About the axis of rotation of the pendulum roller carrier located pendulum rollers are protected in a preferred manner at too low centrifugal force against a radial displacement radially inward. For this purpose, corresponding stops, for example, soft stop buffer, spring elements or the like may be provided.

The proposed centrifugal pendulum has between pendulum mass carrier and pen- del rolls on a circumferentially effective stop damping device. As a result, the roll angle of the spherical rollers on the pendulum roller tracks is elastically limited, so that hard attacks are avoided. This can lead to a reduction in noise of the centrifugal pendulum and to a longer life of the centrifugal pendulum.

According to an advantageous embodiment of the pendulum roller carrier of a centrifugal pendulum is formed from at least two disc parts, between which the spherical rollers are housed axially in a support section. In this case, the stop damping device may be formed between in the spherical roller carrier, for example, in both disc parts axially opposite, circumferentially arcuately elongated slots and in the slots axially engaging pin of the spherical rollers. Here, the arcuate design of the slots is designed such that a movement of the spherical rollers along the predetermined runways between the elastic end stops is not hindered. The pins or projections may be connected to an elastomeric body, such as a Elastomer ring, which may be open on both sides or hat-shaped, be surrounded. The elastomer body comes into contact with the corresponding walls at the end stops of the elongated holes in the circumferential direction and thus elastically limits the rolling path of the spherical rollers. Alternatively or additionally, stop bumps such as elastomeric body, spring elements or the like elastic limit the runway of the rolling elements on the peripheral walls of the slots elastic stops.

To protect the elastomer bodies arranged around the pins, they can be sheathed with a sleeve, for example of hard plastic or metal. The sleeve may be open on both sides or have a hat shape.

According to another embodiment of a centrifugal pendulum with the pendulum rollers between disc parts receiving pendulum roller support the stop damping device may be formed by the spherical rollers are formed from a endsei- tig each pin forming a pin and a surrounding mass body. The pin passes axially through slots of the disc parts. An elastomer body is arranged between the pin and the mass body. In this way, a stop of the pins is elastically damped on circumferential walls of the elongated holes between the pin and the mass body.

According to a further embodiment, the stopper damping device may be provided between the spherical rollers and the pendulum roller tracks. For this purpose, the stop damping device may be formed from an annular elastomer body arranged over the circumference of the spherical rollers, wherein the elastomer body has a predetermined roll angle of the spherical rollers relative to a pendulum roller track of the pendulum roller carrier rolls in a groove of the pendulum roller conveyor and abuts when the roll angle is exceeded on the pendulum roller carrier. In this case, the elastomeric body may be guided in a groove of the roller track opposite groove of the spherical roller. Alternatively, the elastomeric body can be sunk completely in the groove and radially guided over it a guide ring made of metal or hard plastic in the opposite grooves.

The centrifugal pendulum is tuned to at least one predetermined order of vibration, for example, a main vibration order of the internal combustion engine. If a cylinder deactivation is provided in the internal combustion engine, the centrifugal pendulum can be tuned to a plurality of oscillation orders, namely to the oscillation order of the full number of cylinders and to the oscillation orders of the internal combustion engine with the other cylinders operated. This can be provided for example by different masses of the spherical rollers, different pendulum rollerways and / or the like.

According to an advantageous embodiment, at least one contact area between spherical rollers and disk parts may be heat and / or surface treated. For example, corresponding contact areas, for example protrusions of the spherical rollers, pins and / or the areas of the window parts or the entire components located in the support sections - disc parts and / or spherical rollers can be hardened, preferably surface hardened. Alternatively or additionally, coatings, for example layers of diamond-like carbon (DLC), may be provided on at least one contact area. Alternatively or additionally a part of the rolling surfaces or all Wälzflächen be appropriately heat or surface treated.

The disc parts may form in a support portion, in which the spherical rollers are distributed over the circumference, a common for all spherical rollers closed or closed separately for each spherical roller or open, for example by a radially outer gap or recesses in the disc parts cage. The proposed hydrodynamic torque converter is operatively disposed about an axis of rotation between a crankshaft of an internal combustion engine and a transmission input shaft of a transmission. The torque converter may comprise a housing, for example a toroidal housing, which is arranged around a transmission input shaft. The housing may be mounted on a stator spigot formed, for example, in the form of a tubular section and sealed outwardly with respect thereto. The housing may be rotationally driven by the crankshaft, wherein in the housing an impeller may be integrated. For this purpose, can be added to a preformed converter shell fins, for example, hung in the housing and be soldered tight.

By means of a hydraulic fluid stored in the housing, for example ATF, a turbine wheel is driven by the impeller. The turbine wheel is rotationally connected to the transmission input shaft. In that regard, the impeller serves as an input part and the turbine wheel as an output part of the torque converter. Between Impeller and turbine, a stator by means of a freewheel housing fixed, for example, be accommodated on Leitradstutzen.

To bridge the hydrodynamic coupling between impeller and the turbine between a pump and turbine effectively arranged Wandleruberbruckungskupplung is provided, which transmits the torque flow frictionally engaged in the closed state from the housing to the transmission input shaft, in the open state, the hydrodynamic coupling between impeller and turbine and in the slipping state the torque is divided into a torque transmitted via the torque converter lock-up clutch and a part-torque transmitted via the hydrodynamic coupling. The converter lockup clutch is preferably effected by changes in the flows or pressures of the fluid held in the housing. The flows of the fluid are controlled from the outside by means of corresponding control devices and can be supplied and removed via openings, for example in the transmission input shaft, gaps between the transmission input shaft and Leitradstutzen and / or the like. The torque converter lockup clutch may be a multi-plate clutch disposed between the housing and the turbine wheel. The torque converter lockup clutch may be a friction clutch arranged between the housing and the turbine wheel, for example a multi-plate clutch or may be formed from a single friction lining forming a frictional connection with a counter friction surface. The torque converter lockup clutch may include an axially displaceable piston with a friction surface that can form a frictional engagement with a counter friction surface. Here, the piston can be rotatably connected to the turbine and form a frictional connection with a counter-friction surface arranged on the housing. Alternatively, the piston can be connected in a rotationally fixed manner to the turbine wheel and form a frictional connection with a counter-friction surface of the turbine wheel. According to an advantageous embodiment, the converter pressure coupling is arranged between outer peripheries of the impeller and of the turbine wheel. As a result, additional components, such as fins of the Wandleruberbruckungskupplung, pistons and the like can be saved. Furthermore, by eliminating these components additional axial space available, so that the torque converter can be axially formed particularly narrow. The turbine wheel of the lockup clutch formed in this way is designed to be so stiff that the forces occurring at the lockup clutch at the frictional engagement radially outside the vanes of the turbine wheel can be transmitted. The operation of the lockup clutch takes place in a preferred manner by setting different fluid flows or differential pressures on both sides of the turbine shell. The turbine wheel can be rotatably mounted on the transmission input shaft and axially limited displaceable. For example, the bearing can be provided by means of a bushing which seals the transmission input shaft relative to the turbine wheel so that different fluid flows or flow directions or pressure differences can be set for controlling the torque converter lockup clutch between turbine wheel and pump wheel on the one hand and the remaining volume of the housing on the other hand.

The torque converter further includes the proposed centrifugal pendulum and optionally a torsional vibration damper. For improved vibration isolation of Torsional oscillations, improved protection of the centrifugal pendulum, for improved space utilization and the like In particular in a design of the converter lockup clutch with friction surfaces integrated radially outward into the turbine wheel and impeller, pendulum masses or spherical rollers of the centrifugal pendulum can be arranged at the radial height of the converter lockup clutch. As a result, axial space can be saved, for example, by axial overlap of the centrifugal pendulum and the Wandlertorus.

According to an advantageous embodiment of the torque converter of the pen dolollerenträger taken on a hub, for example, be riveted with this. The hub is rotationally connected to the transmission input shaft and has for this purpose, for example, an inner profile such as internal toothing, which forms a rotational lock with an outer profile such as external toothing of the transmission input shaft. Contrary to the direction of action of the torque converter from the input part to the output part with the turbine downstream centrifugal pendulum, this can be arranged axially between one of the crankshaft facing wall of the housing and the turbine wheel, ie in geometrical arrangement between the input part and turbine wheel. The hub of the centrifugal pendulum pendulum can thereby form a rotational circuit with an end-side portion of the transmission input shaft and thus form the output part of the torque converter.

In a preferred embodiment, the pendulum roller carrier is designed in several parts. For example, this may consist of a pendulum rollers axially leading first disc part and a second, the pendulum rollerways having disc part as Be formed guide flanges. The two disc parts can be riveted radially within the spherical rollers after their introduction into a work space formed by the disc parts, for example, riveted. In an advantageous embodiment, the first of the two interconnected disc parts is connected to the hub.

An in the effective direction between the turbine wheel and centrifugal pendulum optionally arranged torsional vibration damper has an input part, which is connected to the turbine wheel, for example, riveted. The riveting of this riveting is preferably provided radially within the fins of the turbine wheel. The input part may be stamped and formed from an annular sheet metal part. Here, the elements of the spring device, for example, short Schraubendruck- or Bogenfe- countries, may be provided radially on the outside surrounding the sheet metal part. The output part of the torsional vibration damper may be connected to the pendulum roller carrier directly or to the hub. Advantageously, the pendulum roller carrier and the output part of the torsional vibration damper can be connected together with the hub, for example, riveted. The hydrodynamic torque converter with lockup clutch, centrifugal pendulum and the optional torsional vibration damper can be designed as a separate unit that is threaded during assembly of the drive train of a motor vehicle or on the transmission input shaft. The invention will be explained in more detail with reference to the Ausführungsbei- game shown in Figures 1 to 7. Showing: the upper part of a torque converter arranged around a rotation axis,

2 is a partial view of the centrifugal pendulum pendulum of FIG. 1,

one compared to the spherical rollers of Figures 1 and 2 modified

Pendulum roll in section,

a detail of a relative to the centrifugal pendulum pendulum of Figures 1 and 2 abge changed centrifugal pendulum with modified stop damping device,

a detail of a compared to the centrifugal pendulum pendulum of Figure 1 to 4 modified centrifugal pendulum with modified stop damping device,

a detail of a relative to the centrifugal pendulum pendulum of Figure 1 to 5 modified centrifugal pendulum with modified stop damping device a modified detail of the centrifugal pendulum pendulum of Figure 6.

FIG. 1 shows the upper part of the torque converter 1, which is rotatable about the axis of rotation d of the transmission input shaft 6. The housing 14 accommodates the impeller 3, the turbine 10, the lockup clutch 9, the centrifugal pendulum 4 and the torsional vibration damper 13 and is at least partially filled with hydraulic fluid to produce the hydrodynamic coupling of the impeller 3 with the turbine 10 during operation. The housing 14 is rotatably connected by means of the fastening means 15 by means of a flexplate or the like and axially elastically connected to the crankshaft of an internal combustion engine. The impeller 3 is integrated in the housing 14. The housing 14 is formed from the converter shell 16 and the wall 17 with the axial projection 18, which are radially connected externally sealed together, for example, welded.

The lockup clutch 9 is integrated in the turbine 10 and the impeller 3. For this purpose, the turbine wheel 10 is radially expanded and has the coupling flange 19. The ring section 20 is provided at the transition between the projection 21, which is welded to the axial projection 18, of the converter shell 16 and the impeller 3. On the coupling flange 19 and / or on the ring portion 20 of the friction lining 22, for example, a paper coating is provided which forms the frictional engagement with the Gegenreibfläche the converter lock-up clutch 9. The lockup clutch 9 is actuated by means of a fluid flow between the enclosed between the turbine 10 and impeller 3 chamber 23 on the one hand and separated from this by means of the sleeve 24 between the transmission input shaft 6 and turbine 10 chamber 25, wherein the fluid flow through the gap 26 and the hollow bore 27 of Transmission input shaft 6 is supplied or removed. The fluid flow flows through the chambers 23, 25 with different flow velocities of the turbine wheel 10, so that this buoyancy is maintained and opened. The fluid flow is maintained especially when the converter lock-up clutch 9 is open and slipping. In a particularly advantageous manner, grooves such as cooling grooves are provided in the friction lining 22 and / or in the counter-friction surface thereof which, even with the converter lock-up clutch 9 closed, have a predetermined benen fluid flow maintained and thus cool the lockup clutch 9 in the region of the friction engagement.

The centrifugal pendulum 4 is arranged in the chamber 25 axially between the wall 17 and the turbine wheel 10 and occupies substantially the radially available space to the inner periphery of the axial projection 18 a. The centrifugal force pens 4 serves as an output part of the torque converter 1 and has distributed over the circumference of spherical rollers 29 and the pendulum roller carrier 30. The pendulum roller carrier 30 is formed from the two disc parts 31, 32 which are radially connected within the pendulum rollers 29 by means of the rivets 33. The carrier section 34 formed radially outside the rivet 33 accommodates the spherical rollers 29 distributed over the circumference. The spherical rollers 29 have axially expanded pin 49, which extend radially into the arcuate slots 36 of the disc parts 31, 32. The pins 49 and the elongated holes 36 form the stops of the spherical rollers 29 along their movement on the pendulum roller conveyor 35 and thus limit their roll angle. The stops are elastically damped to form the stopper damping device 50. For this purpose, the annular elastomer body 51 are received on the pin 49, which form a soft stop against the peripheral walls of the slots 36. The arcuate shape of the oblong holes 36 follows the shape of the pendulum roller track 35, so that the pins 49 move in the region of the permitted roll angle of the spherical rollers 29 essentially without contact between the peripheral stops in the slots 36.

The hub 5 is rotationally connected with the front end region of the transmission input shaft 6 as toothed and receives the centrifugal pendulum 4. This is the disk member 31 is received on the radially enlarged hub flange 38 of the hub 5 by means of the same rivet 38a as the output member 37 of the optional torsional vibration damper 13. The output member 37 of the torsional vibration damper 13 and the input member 39 connected to the turbine 10 by means of the rivet 40 are against the action of Distributed over the circumference arranged spring elements 41 such as helical compression springs relative to each other rotatable about the rotation axis d, so that the torsional vibration damper 13 remaining torsional vibrations, which still remain after the hydraulic coupling between impeller 3 and turbine 10 and by the absorber function of the mass of the turbine wheel, dampens. The downstream centrifugal pendulum 4 in turn removes the remaining after the torsional vibration damper 13 torsional vibrations.

The torsional vibration damper 13 is accommodated radially in the region of the draw-in 42 of the turbine wheel 10 between its mounting on the transmission input shaft 6 and its belly with the maximum axial expansion of the fins 43 in a space-saving manner. The input part 39 is outside of the diameter of the spring elements 41 placed around this at least their outer diameter cross-over, so that they are radially supported and axially lost captive in the input part 39. For the sake of completeness it should be mentioned that between impeller 3 and turbine wheel 10 to increase the torque at differential speeds, the stator 46 is arranged, which is received by means of the freewheel 47 on the Leitradstutzen 48.

FIG. 2 shows a detail of the centrifugal pendulum 4 of FIG. 1 in a view. The disk part 31 has slots 36 distributed over the circumference, in which the pins 49 of the spherical rollers 29 with the surrounding elastomeric bodies 51 during Abroll movements of the spherical rollers 29 on the pendulum roller 35 of the disc member 31 relocate. The slots 36 are simulated the course of the pendulum roller 35 and have walls with peripheral stops 52, the roll angle of the spherical rollers 29 by abutment of the pin 49 by interposition of the

Elastomer body 51 elastically limit and dampen.

In contrast to the spherical rollers 29 shown in the centrifugal pendulum 4 of Figures 1 and 2, Figure 3 shows the shuttle roller 29a in section. In contrast to these, the pendulum roller 29 a axially extended pin 49 a, which are surrounded by an elastomeric body 51 a, which is surrounded by the sleeve 53 a radially outward. The sleeve 53 a is used to protect the elastomeric body 51 a and may be formed of a harder plastic material than the elastomeric body 51 a or metal. The sleeve 53a may be pressed onto the elastomeric body or integrally connected thereto, for example by vulcanization.

FIG. 4 shows a partial view of the centrifugal pendulum 104 modified relative to the centrifugal force pendulum 4 of FIGS. 1 and 2. In contrast to the centrifugal pendulum 4, the pendulum rollers 129 of the centrifugal pendulum 104 are formed with pins 149 without elastomeric bodies. To form the stop damping device 150, the stops 152 of the elongated holes 136 are provided with elastomeric bodies 151. These are by means of undercuts with recesses 154 of the disk part 131 forming nipples 155 fixedly connected to the disk part 131. Figure 5 shows the upper part of the centrifugal pendulum 4, 104 of Figures 1, 2 and 4 similar centrifugal pendulum 204 in section. In contrast to these, in the centrifugal pendulum pendulum 204, the pendulum roller 229 is formed in several parts from the pin 256, the mass body 257 and the elastomer body 251. The pin 256 extends axially through the slotted parts 236 of the disk parts 231, 232 and, by forming the stopper damping device 250, takes up the elastomer body 251 over its circumference. On the outer circumference of the elastomer body 251 of the mass body 257 is elastically received, which rolls on the pendulum roller conveyor 235 of the disk part 231 and forms a rolling contact with this under centrifugal force, which is limited by attacks of the pin 256 on peripheral attacks of the slots 236.

FIG. 6 shows the upper part of the centrifugal force pendulum 304 modified in comparison to the centrifugal force pendulums 4, 104, 204 of FIGS. 1, 2, 4 and 5 in section. In the centrifugal force pendulum 304, the oblong holes in the disc parts fall away, so that optionally a closed cage for the spherical rollers 329 can be provided from the disc parts 331, 332. For example, in the exemplary embodiment shown, a gap existing between the disk parts 331, 332 is closed by means of a weld seam 358. The stopper damper 350 is formed between the spherical rollers 329 and the shuttle roller 335. For this purpose, 335 opposite grooves 359, 360 are provided in the spherical rollers 329 and in the pendulum roller conveyor, between which the elastomeric body 351 is effective. The elastomer body 351 can serve as an axial guide and forms on one of the disk parts 331, 332 at the end of the pendulum roller conveyor 335 an elastic stop for limiting the roll angle of the spherical rollers 329 in both circumferential directions. For improved axial guidance of the spherical rollers 329 relative to the pendulum roller conveyor 335 may - as shown in detail in Figure 7 - between the grooves 359, 360 a closed or open ring member 361 may be provided which is made for example of plastic or metal, the radially outside of the elastomer body 351 a is aufgenonnnnen in the groove 359 of the pendulum roller 329. Here, the ring member 361 forms the stop against one or both disc parts 331, 332 upon reaching the maximum roll angle of the spherical rollers 329th

Characteristics list torque converter

impeller

centrifugal pendulum

hub

Transmission input shaft

Converter lockup clutch

turbine

Drehschwingungsdannpfer

casing

fastener

converter shell

wall

approach

coupling flange

ring section

approach

friction lining

chamber

Rifle

chamber

gap

hollow bore

Spherical roller

Spherical roller carrier

disk part

rivet

support section

Shuttle runway

Long hole output portion

hub flange

a rivet

introductory

rivet

spring element

collection

lamella

stator

freewheel

Leitradstutzen

spigot

a cone

Stop damper

elastomer body

a Elastomer body

attack

a sleeve

4 centrifugal pendulum

9 shuttle roller

1 disc part

6 slot

9 cones

0 stop damping device1 elastomer body

2 stop

4 recess

5 nipples

4 centrifugal pendulum

9 shuttle roller

1 disc part

2 disc part

5 pendulum roller conveyor

6 slot 250 stop damping device

251 Elastomer body

256 pen

257 mass bodies

304 centrifugal pendulum

329 pendulum roller

331 disk part

332 disc part

335 shuttle runway

350 stop damping device

351 Elastomer body

351 a Elastomer body

358 weld

359 groove

360 groove

361 ring part

d rotation axis

D rotation axis

Claims

claims

1 . Centrifugal pendulum (4, 104, 204, 304) with a pendulum roller carrier (30) arranged around a rotation axis (d) and spherical rollers (29, 29a, 129, 229, 329) distributed over the circumference, which are secured against loss on the pendulum roller carrier (30). are formed and under centrifugal force of about the rotational axis (d) rotating pendulum roller carrier (30) by means of pendulum rollerways (35, 235, 335) with the spherical roller carrier (30) form a rolling contact, characterized in that between spherical roller carrier (30) and spherical rollers (29, 29a, 129, 229, 329) a stop damping device (50, 150, 250, 350) is provided.

2. centrifugal pendulum (4, 104, 204) according to claim 1, characterized in that the stop damping device (50, 150, 250) between in the spherical roller carrier (30) provided in the circumferential direction arcuate elongated holes (36, 136, 236) and in the elongated holes (36, 136, 236) axially engaging pin (49, 49a, 149) of the spherical rollers (29, 29a, 129, 229) is formed.

3. centrifugal pendulum (4) according to claim 1, characterized in that around the pins (49, 49 a) an elastomeric body (51, 51 a) is arranged.

4. centrifugal pendulum (4) according to claim 1, characterized in that the

Elastomer body (51 a) with a sleeve (53 a) are sheathed.

5. centrifugal pendulum (204) according to claim 1, characterized in that the spherical rollers (229) from a pin containing the pin (256) and a surrounding mass body (257) are formed, wherein between the pin (256) and the mass body ( 257) an elastomeric body (251) is arranged.

6. centrifugal pendulum (104, 204) according to one of claims 2 to 5, characterized in that at circumferential stops (152) of the slots (136) formed as a stop buffer Elastomerkorper (151) are provided.

7. centrifugal pendulum (304) according to claim 1, characterized in that the stop damping device (350) from an over the circumference of the spherical rollers (329) arranged annular elastomeric body (351) is formed, wherein the elastomeric body (351) over a predetermined Rolling angle of the spherical rollers (329) relative to a pendulum roller conveyor (335) of the pendulum roller carrier in a groove (360) of the pendulum roller conveyor (335) unrolls and abuts when the roll angle is exceeded on the pendulum roller carrier.

8. Hydrodynamic torque converter (1) having a housing (14) arranged around a rotation axis (d) and an impeller (3) integrated into the housing (14), wherein the housing (14) has a turbine wheel (10) arranged rotatable relative thereto; a between the impeller (3) and turbine (10) operatively arranged lock-up clutch (9), optionally a torsional vibration damper (13) and a centrifugal pendulum (4, 4a, 4b, 4c) according to one of claims 1 to 7 receives.

9. Hydrodynamic torque converter (1) according to claim 8, characterized in that the centrifugal pendulum (4, 4a, 4b, 4c) is formed as an output part of the torque converter (1).

10. Hydrodynamic torque converter (1) according to claim 8 or 9, characterized in that the converter lock-up clutch (9) between outer peripheries of the impeller (3) and the turbine wheel (10) is arranged.