DE102015215910A1 - Centrifugal pendulum and hydrodynamic torque converter with centrifugal pendulum - Google Patents

Abstract

The invention relates to a centrifugal pendulum (4) and a hydrodynamic torque converter (1) having a housing (14) arranged around the transmission input shaft (6), an impeller (3) integrated in the housing (14), the housing (14) being opposite one another this rotatably arranged turbine wheel (10), between the impeller (3) and turbine wheel (10) effectively arranged converter lockup clutch (9), optionally a torsional vibration damper (13) and a centrifugal pendulum (4) receives. To improve the effect of the centrifugal pendulum (4) at least one rolling surface between pendulum elements (29) and pendulum tracks (35) is provided with a radial profiling.

Description

The invention relates to a centrifugal pendulum and a torque converter containing this with a between a crankshaft of an internal combustion engine and a transmission input shaft of a transmission effectively arranged hydrodynamic torque converter with a arranged around the transmission input shaft housing, an integrated pump in the housing, wherein the housing is rotatable relative to this arranged a turbine wheel , a converter lock-up clutch operatively arranged between the impeller and the turbine wheel, and possibly 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. Due to this pendulum suspension, the pendulum masses in the centrifugal force field of the rotating support member form a speed-adaptive torsional vibration damper by withdrawing the pendulum mass energy through corresponding deflection of the drive train during torque peaks and feed at torque minima.

For example - as from the WO2014 / 082629 A1 known - be arranged axially between two side parts which form the support member, distributed over the circumference pendulum masses. Alternatively - as from the DE 10 2012 221 949 A1 known - pendulum mass parts be arranged on both sides of the support member. Axial opposing pendulum mass parts are connected by means of connecting means with each other to pendulum masses, wherein the connecting means pass through corresponding recessed recesses of the support member.

A centrifugal pendulum can - as for example with reference to the above-mentioned publications WO2014 / 082629 A1 . DE 10 2012 221 949 A1 disclosed - be provided on a one-mass flywheel, for example, a single-mass flywheel made of sheet metal. For example, from the publications WO2014 / 023303 A1 and DE 10 2013 201 981 A1 known, one or more centrifugal pendulum on a torsional vibration damper, according to the document WO2014 / 114 280 A1 on a clutch disc, according to the document EP 2 600 030 A1 be provided on a hydrodynamic torque converter, on a housing of a friction clutch or at 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 impeller and turbine wheel is closed so that the torque is transmitted directly from the housing to the transmission input shaft, bypassing the converter components, thus eliminating the deteriorating efficiency of the converter components 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 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, is from the WO 2010/043194 A1 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, said centrifugal pendulum is connected directly to the turbine wheel. From the DE 198 04 227 A1 is a torque converter with at one of the lockup clutch associated torsional vibration damper arranged balancing masses known to roll on pendulum tracks. The object of the invention is the Development of a centrifugal pendulum and a torque converter with a centrifugal pendulum. In particular, the object of the invention to provide a centrifugal pendulum with an improved unwinding of the pendulum elements or spherical rollers of a pendulum bearing on the associated pendulum track.

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 contains a pendulum element carrier arranged about a rotation axis and distributed over the circumference arranged on this pendulum elements.

The pendulum element carrier can be formed from a single disk part designed as a pendulum flange, which accommodates pendulum elements arranged distributed on both sides over the circumference. Axially opposed pendulum elements can be firmly connected to each other. The pendulum element carrier can be formed from two or more disc parts, wherein in each case two disc parts have axially between them pendulum sections, between which are distributed axially and distributed over the circumference pendulum elements.

The pendulum elements may be formed as spherical rollers, which have a pendulum track, with which they roll on the pendulum element carrier and thus perform monofilar pendulum movements relative to the pendulum element carrier. The pendulum elements may be formed as bifilar pendulum masses suspended on the pendulum element carrier, wherein the pendulum masses are suspended by means of two circumferentially spaced pendulum bearings on the pendulum element carrier. The pendulum bearings are designed as complementary to each other formed pendulum tracks of the pendulum masses and the pendulum element carrier on which an arranged between the pendulum tracks of a pendulum bearing rolling elements, for example, a pendulum roller rolls.

The pendulum elements may be formed, for example, as discs made of sheet metal and round, elliptical, be formed in a teardrop or similar shape. The pendulum elements are captive secured to the pendulum element carrier. Under the action of centrifugal force of the pendulum element carrier rotating about the axis of rotation, the pendulum elements form a rolling contact by means of a rolling surface with a rolling surface of a pendulum track of the pendulum element carrier. For example, the pendulum element carrier may be formed in two parts from disc parts such as side parts made of sheet metal, wherein the pendulum elements can be accommodated axially between them in individual pendulum spaces separated from each other. In this case, for example, a disc part contains the pendulum tracks, for example, by its outer circumference punched out and transformed accordingly. The other disc part is applied to this and serves for the axial securing of the pendulum elements. Radially within the pendulum elements can have one of the disc parts, such as the disc part with the pendulum tracks an axial collar for radially limiting the pendulum spaces. 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 crank 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 dual clutch, an electric machine or the like integrated.

The rolling surface of the pendulum elements in this case has a rolling contact over the circumference with respect to the rolling surface of the pendulum track.

The centrifugal pendulum can be formed from a pendulum element carrier with pendulum masses which are pendulum-like in centrifugal force field. Under the influence of centrifugal force, pendulum elements shift against the pendulum tracks and shift there for the eradication of torsional vibrations. About the axis of rotation of the pendulum element carrier located pendulum elements 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 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 pendulum elements or pendulum masses, different raceways or pendulum tracks and / or the like.

In order to improve the rolling movement of the pendulum elements, in particular in rooms with a fluid such as converter fluid or fluid of a wet-operated friction clutch or double clutch relative to the shuttle element carrier, a radial is at least one of the rolling surfaces Profiling provided. The at least one radial profiling can be simulated in accordance with a profile of a vehicle tire which avoids or reduces the aquaplaning effect. Accordingly, profile shapes used there can also be advantageous in the proposed profiling. In this case, radial profilings can be provided on the rolling surfaces of the pendulum elements and / or the pendulum raceways. When using profilings in both rolling surfaces, similar profilings can be provided identically or in opposite directions or different profilings from one another.

According to an advantageous embodiment, a profiling can be formed from at least one circumferential groove. For example, several, preferably two axially spaced, mutually parallel grooves form such a profiling. Alternatively, the grooves can not be arranged parallel to each other, for example, at different angles relative to the axis of rotation of the centrifugal pendulum. Such profiles can be designed as discrete circumferential or intersecting grooves. In this case, a displacement of fluid during a rolling movement of the roller pendulum takes place preferably in the grooves in the circumferential direction.

According to a further alternative or additional embodiment of a profiling can be provided to provide at least two, preferably a plurality of distributed over the circumference arranged transverse grooves. The transverse grooves may be parallel to the axis of rotation of the centrifugal pendulum or inclined relative to this. The transverse grooves can be arranged parallel to one another or inclined relative to one another and thereby, for example, cross over one another. Furthermore, the transverse grooves may be linear, curved or V-shaped. A displacement of fluid during a rolling movement of the pendulum elements takes place in profiles with transverse grooves in a preferred manner in the axial direction.

According to a further embodiment can be provided on the pendulum elements or with appropriate design of the pendulum element carrier there - profilings having curved grooves, wherein the curved grooves have a rolling surface in the circumferential direction and an opening on an end side of the pendulum elements groove part. The arc between the two groove parts can be rectangular, acute or obtuse. These curved grooves can be arranged distributed over the circumference, wherein in each case on the same circumference or in the circumferential direction offset two each opening on an end face of the pendulum elements rows of curved grooves can be provided. According to a further specified embodiment of curved grooves curved over the circumference first grooves with in the rolling direction of the pendulum elements first opening on the rolling surface Nutteil with second curved grooves with alternating first opening at one end groove portion. In this way, for example, in an axial sequence with distributed on the same circumference arranged first and second grooves distributed over the circumference, centrally raised lozenges on the rolling surface, which come into rolling contact with the rolling surface of the pendulum track and limited by the grooves, curved inward Have side surfaces. In this way, a particularly effective displacement of fluid in both the circumferential direction and in the axial direction can be effected on both end faces of the pendulum elements.

According to an advantageous embodiment, a profiling can be formed from over the circumference and arranged axially distributed, separate openings. Here, the openings may be circular, oval, circumferentially or axially limited groove-shaped or formed in a similar manner.

The introduction of the profiles can be done by machining or shaping, for example by means of rolling, knurling, impact method or the like.

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 Leitradstutzen formed for example in the form of a pipe section and sealed against the outside. 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 taken on Leitradstutzen.

To bridge the hydrodynamic coupling between the pump impeller and the turbine wheel, a pump impeller and turbine wheel are effectively arranged Lockup clutch 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 the impeller and turbine and switches in the slipping state, the torque in a transmitted via the lockup clutch part torque and a transmitted over the hydrodynamic coupling torque part , 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 appropriate 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 lockup clutch may include an axially displaceable piston having a friction surface that can frictionally engage a counter friction surface. Here, the piston can be rotatably connected to the turbine and form a frictional engagement 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 lockup clutch is disposed between outer peripheries of the impeller and the turbine wheel. As a result, additional components, such as fins of the converter lockup clutch, piston 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 bush which seals the transmission input shaft relative to the turbine wheel so that different fluid flows or flow directions or pressure differences for controlling the torque converter lockup clutch can be set between the turbine wheel and impeller on the one hand and the remaining volume of the housing on the other hand.

The torque converter further includes a centrifugal pendulum and optionally a torsional vibration damper. For improved vibration isolation of torsional vibrations, improved protection of the centrifugal pendulum, for improved space utilization and the like, the centrifugal pendulum between turbine and transmission input shaft is arranged. The torsional vibration damper can be effectively arranged between the turbine wheel and the transmission input shaft or between the turbine wheel and the centrifugal pendulum. This means that the centrifugal pendulum is connected downstream of both the turbine wheel and the lockup clutch. Furthermore, if necessary, the centrifugal pendulum downstream of the torsional vibration damper. This means that a pendulum element carrier of pendulum masses or pendulum elements can be connected to the output part of the torsional vibration damper or formed from this or the carrier is rotationally connected directly or by means of a hub with the transmission input shaft. The turbine wheel can act vibration-damping by means of its mass. Furthermore, the optionally used torsional vibration damper dampens with respect to torsional vibrations, so that the centrifugal pendulum can be designed for remaining residual vibrations. This is particularly advantageous because torsional vibration peaks that can lead to attacks and high loads of centrifugal pendulum can be avoided or at least reduced. Furthermore, it may be advantageous that the centrifugal pendulum, which is effectively arranged at this point, can be designed specifically for the remaining residual vibrations.

In particular, in an embodiment of the converter lockup clutch with friction surfaces integrated radially outside into the turbine wheel and the impeller, pendulum masses or oscillating elements 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, the pendulum element carrier can be accommodated on a hub, for example riveted to it. The hub is rotationally connected to the transmission input shaft and has, for example, an inner profile such as internal teeth, which with a External profile as external teeth of the transmission input shaft forms a rotational lock. 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, so in geometric arrangement between the input part and turbine wheel. The hub of the centrifugal pendulum can thereby form a rotational circuit with an end portion of the transmission input shaft and thus form the output part of the torque converter.

The pendulum element carrier of the preferably designed as a roller pendulum centrifugal pendulum can be integrally formed. For this purpose, the pendulum elements on the pendulum tracks on both sides radially overlapping sections, so that they are axially guided relative to the shuttle element carrier. Such pendulum elements are mounted in the pendulum tracks forming sections of the pendulum element carrier from radially inside. A captive can exclude a shift radially inward. In a preferred embodiment, the shuttle element carrier is designed in several parts. For example, this may be formed from a pendulum elements axially leading first disc part and a second, the pendulum tracks having disc part. The two disc parts can be riveted radially within the pendulum elements after their introduction into a working space formed by the disc parts, for example. In an advantageous embodiment, the first of the two interconnected disc parts is connected to the hub.

The arranged in the effective direction between the turbine wheel and centrifugal pendulum torsional vibration damper has an input part, which is connected to the turbine wheel, for example, riveted. The riveting circle of this riveting is preferably provided radially within the lamellae of the turbine wheel. The input part may be stamped and formed from an annular sheet metal part. In this case, the elements of the spring device, for example, short helical or bow springs, 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 shuttle element carrier directly or to the hub. Advantageously, the pendulum element 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 torsional vibration damper may be formed 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 is based on the in the 1 to 7 illustrated embodiment illustrated. Showing:

1 the upper part of a torque converter arranged around a rotation axis,

2 a partial view of the centrifugal pendulum of 1 .

3 the pendulum elements of 1 and 2 in view,

4 one opposite the pendulum element of 3 modified pendulum element in view,

5 one opposite the pendulum elements of 3 and 4 modified pendulum element in view,

6 one opposite the pendulum elements of 3 to 5 Modified pendulum element in view
and

7 a detail of one opposite the centrifugal pendulum of the 1 modified centrifugal pendulum on average.

The 1 shows the upper part of the about the axis of rotation d of the transmission input shaft 6 rotatably arranged torque converter 1 , The housing 14 takes the impeller 3 , the turbine wheel 10 , the lockup clutch 9 , the centrifugal pendulum 4 and the optional torsional vibration damper 13 and is to produce the hydrodynamic coupling of the impeller 3 with the turbine wheel 10 at least partially filled with hydraulic fluid during operation.

The housing 14 is by means of the fastening means 15 by means of a flexplate or the like rotatably and axially elastically connected to the crankshaft of an internal combustion engine. The impeller 3 is in the case 14 integrated. The housing 14 is from the converter shell 16 and the wall 17 with the axial approach 18 formed, which are radially connected externally sealed together, for example, welded. The torque converter lockup clutch 9 is in the turbine wheel 10 and the impeller 3 integrated. This is the turbine wheel 10 radially expanded and has the coupling flange 19 on. At the transition between the with the axial approach 18 welded approach 21 the converter shell 16 and the impeller 3 is the ring section 20 intended. On the coupling flange 19 and / or on the ring portion 20 is the friction lining 22 . For example, provided a paper covering, the frictional engagement with the Gegenreibfläche the converter lockup clutch 9 forms. The torque converter lockup clutch 9 is by means of a fluid flow between the turbine between 10 and impeller 3 enclosed chamber 23 on the one hand and of this by means of the socket 24 between transmission input shaft 6 and turbine wheel 10 separated chamber 25 operated, the fluid flow through the gap 26 and the hollow bore 27 the 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 gets a boost and is opened. The fluid flow is in particular when the converter lock-up clutch is open and slipping 9 maintained. In a particularly advantageous manner are in the friction lining 22 and / or provided in its counter-friction surface grooves such as cooling grooves, which also in closed torque converter lockup clutch 9 maintain a predetermined fluid flow and thus the lockup clutch 9 cool in the region of the frictional engagement.

The centrifugal pendulum 4 is in the chamber 25 axially between the wall 17 and the turbine wheel 10 arranged and takes substantially the radially available space to the inner periphery of the axial extension 18 one. The centrifugal pendulum 4 serves as the output part of the torque converter 1 and has circumferentially distributed pendulum elements 29 and the shuttle element carrier 30 on. The pendulum element carrier 30 is from the two disc parts 31 . 32 formed radially inward by means of the rivet 33 connected to each other. The radially outside of the rivet 33 formed carrier section 34 takes the distributed over the circumference arranged pendulum elements 29 each lost on. The disc part 32 has radially outward for each shuttle 29 a pendulum runway 35 on, on which the outer circumference of the pendulum element 29 supported under centrifugal force and rolls on occurring torsional vibrations. Depending on the example in the circumferential direction arcuate design of the pendulum tracks 35 becomes the pendulum element 29 thereby displaced against the centrifugal force to a smaller diameter, so that the transformation of the kinetic energy of a torque peak into potential energy smoothes the course of the torque.

To provide an improved rolling movement of the circumferentially distributed in the fluid of the torque converter 1 arranged pendulum elements 29 to achieve is between the pendulum element carrier 30 and the pendulum elements 29 for improved displacement of the fluid during a rolling movement of the pendulum elements 29 the radial profiling 52 intended. In the illustrated embodiment, the radial profiling 52 in the form of grooves 53 provided in the pendulum element 29 are introduced. The grooves 53 are here as parallel, axially spaced around the shuttle 29 formed circumferential grooves.

The disc part 31 serves the axial securing of substantially at the radial height of the lockup clutch 9 arranged pendulum elements 29 , The pendulum elements 29 are crowned in the contact area to the pendulum tracks. Between the disc parts 31 . 32 is radially outside the gap 36 provided, for example, the dynamic fluid guide on the pendulum elements 29 to improve.

The hub 5 is with the front end portion of the transmission input shaft 6 rotationally connected as toothed and takes the centrifugal pendulum 4 on. This is the disc part 31 on the radially enlarged hub flange 38 the hub 5 by means of the same rivet 38a recorded as the output part 37 of the torsional vibration damper 13 , The starting part 37 of the torsional vibration damper 13 and that with the turbine wheel 10 by means of the rivet 40 connected input part 39 are opposite to the effect 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 after the hydraulic coupling between impeller 3 and turbine wheel 10 as well as remaining by the absorber function of the mass of the turbine wheel, dampens. The downstream centrifugal pendulum 4 in turn, the one after the torsional vibration damper wipes out 13 still remaining torsional vibrations.

The torsional vibration damper 13 is radial in the area of the feeder 42 of the turbine wheel 10 between its storage on the transmission input shaft 6 and its belly with the maximum axial extension of the slats 43 saved space. The entrance part 39 is outside the diameter of the spring elements 41 placed around this at least their outer diameter across, so that they are radially supported and axially captive in the input part 39 are included.

For completeness, it should be mentioned that between impeller 3 and turbine wheel 10 to increase the torque at low speeds of the impeller 3 the stator 46 is arranged, which by means of the freewheel 47 at the Leitradstutzen 48 is included.

The 2 shows a partial view of the centrifugal pendulum 4 of the 1 with removed disc part 31 with a view to the longitudinal direction cut shown pendulum elements 29 and the disc part 32 of the pendulum element carrier 30 , To the outer periphery of the disc part 32 is the axial approach 43 molded, on the inner circumference of the pendulum tracks 35 for the pendulum elements 29 are formed. The shape of the pendulum tracks 35 in the circumferential direction is the pendulum motion of the pendulum elements 29 in the centrifugal force field under the influence of torque oscillations. In the embodiment shown, the pendulum elements 29 circular. These can also form other shapes, for example elliptical or oval shapes, drop shape or the like. Due to the shape of the pendulum tracks 35 , Pendulum elements 29 whose mass and the like are set one or more vibration orders. Due to the axially extended collar 44 on the inner circumference of the disc part 32 become the pendulum elements 29 - contrary to the sketchy representation - each in the areas of their pendulum careers 35 held. In the axial direction have a Wälzkontakt forming pendulum tracks 35 and the surfaces of the pendulum elements 29 rolling surfaces 50 . 51 on that between them with the radial profiling 52 are provided, so that about the profiling 52 Fluid is displaced in the circumferential direction when the pendulum elements 29 on the pendulum tracks 35 or on these arranged rolling surfaces 51 roll off. The profiling 52 is in the form of grooves 53 formed, of which only the front cut groove 53 is visible. The other axially spaced second groove is behind the groove 53 ,

The 3 shows the pendulum element 29 of the 1 and 2 in view with the from the two at the Wälzfläche 50 the pendulum element 29 introduced, axially spaced grooves 53 like longitudinal grooves.

The 4 shows that opposite the pendulum element 29 of the 3 modified pendulum element 29a for the centrifugal pendulum 4 of the 1 and 2 in view. The radial profiling 52a is here distributed over the circumference of the rolling surface 50a arranged grooves 53a formed as transverse grooves on the two end faces 55a of the pendulum element 29a open and thus cause a displacement of fluid in the axial direction, when the pendulum element 29a rolls on the pendulum runway. The 5 shows this opposite the pendulum elements 29 . 29a of the 3 and 4 modified pendulum element 29b in view. The radial profiling 52b is by curved grooves 53b . 54b formed, which have the same shape, but are arranged alternately over the circumference. Here are the curved grooves 53b . 54b one each on the rolling surface 51b opening groove part 56b and one on the front sides 55b opening groove part 57b on. Grooves alternate each other over the circumference 53b moving in the direction of movement of the pendulum element 29b first with the groove part 56b and then with the groove part 57b Contact the rolling surface of the pendulum track, with grooves 54b from where first the groove part 57b and then the groove part 56b contacted the Wälzfläche the pendulum track.

6 shows this opposite the pendulum elements 29 . 29a . 29b of the 3 to 5 modified pendulum element 29c for the centrifugal pendulum 4 of the 1 and 2 in view. In this pendulum element 29c is the radial profiling 52c by means of the openings distributed over the circumference 53c educated. In the embodiment shown, three axially spaced rows form with openings distributed over the circumference 53c the radial profiling 52c at the rolling surface 50c of the pendulum element 29c ,

It is understood that the rolling surfaces of the pendulum elements 29 . 29a . 29b . 29c of the 3 to 6 associated pendulum element carrier 30 ( 1 ) may also have radial profilings.

The 7 shows a detail of one opposite the centrifugal pendulum 4 of the 1 and 2 modified centrifugal pendulum 4d on average. Here is the disc part 31d of the pendulum element carrier 30d with the axial approach 44d provided while the disc part 32d the axial cover for the pendulum elements 29d forms. The radial profiling 52d is here in the rolling surface 51d of the axial approach 44d provided while the rolling surface 50d of the pendulum element 29d is designed essentially plan. It is understood that also the pendulum element 29d may have a radial profiling. In the illustrated embodiment, the radial profiling 52d of the centrifugal pendulum 4d in the form of three equally spaced, circumferential, circumferential grooves 53d educated.

LIST OF REFERENCE NUMBERS

1

 torque converter

3

 impeller

4

 centrifugal pendulum

4d

 centrifugal pendulum

5

 hub

6

 Transmission input shaft

9

 Converter lockup clutch

10

turbine

13

 torsional vibration dampers

14

 casing

15

 fastener

16

 converter shell

17

 wall

18

 approach

19

 coupling flange

20

 ring section

21

 approach

22

 friction lining

23

 chamber

24

 Rifle

25

 chamber

26

 gap

27

 hollow bore

29

 shuttle

29a

 shuttle

29b

 shuttle

29c

 shuttle

29d

 shuttle

30

 Shuttle carrier

30a

 Shuttle carrier

30b

 Shuttle carrier

30d

 Shuttle carrier

31

 disk part

31d

 disk part

32

 disk part

32d

 disk part

33

 rivet

34

 support section

35

 Pendulum career

36

 gap

37

 output portion

38

 hub flange

38a

 rivet

39

 introductory

40

 rivet

41

 spring element

42

 collection

43

 lamella

44

 approach

44a

 approach

44d

 approach

45

 collar

46

 stator

47

 freewheel

48

 Leitradstutzen

50

 rolling surface

50a

 rolling surface

50b

 rolling surface

50c

 rolling surface

50d

 rolling surface

51

 rolling surface

51b

 rolling surface

51d

 rolling surface

52

 profiling

52a

 profiling

52b

 profiling

52c

 profiling

52d

 profiling

53

 groove

53a

 groove

53b

 groove

53c

 opening

53d

 groove

54b

 groove

55a

 front

55b

 front

56b

 groove part

57b

 groove part

d

 axis of rotation

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• WO 2014/082629 A1 [0003, 0004]
• DE 102012221949 A1 [0003, 0004]
• WO 2014/023303 A1 [0004]
• DE 102013201981 A1 [0004]
• WO 2014/114280 A1 [0004]
• EP 2600030 A1 [0004]
• WO 2010/043194 A1 [0007]
• DE 19804227 A1 [0007]

Claims (10)

Centrifugal pendulum ( 4 . 4d ) with a about an axis of rotation (d) arranged pendulum element carrier ( 30 . 30d ) and distributed over the circumference arranged pendulum elements ( 29 . 29a . 29b . 29c . 29d ), which is secured against loss on the pendulum element carrier ( 30 . 30d ) are received and under centrifugal force of about the axis of rotation (d) rotating pendulum element carrier ( 30 . 30d ) by means of a rolling surface ( 50 . 50a . 50b . 50c . 50d ) with a rolling surface ( 51 . 51d ) of a pendulum track ( 35 ) of the pendulum element carrier ( 30 . 30d ) form a rolling contact, characterized in that at least one of the rolling surfaces ( 50 . 50a . 50b . 50c . 51d ) a radial profiling ( 52 . 52a . 52c . 52d ) having. Centrifugal pendulum ( 4 . 4d ) according to claim 1, characterized in that a profiling ( 52 . 52d ) from at least one circumferential groove ( 53 . 53d ) is formed. Centrifugal pendulum ( 4 . 4d ) according to claim 2, characterized in that the radial profiling ( 52 . 52d ) of at least two axially spaced, mutually parallel grooves ( 53 . 53d ) is formed. Centrifugal pendulum ( 4 ) according to one of claims 1 to 3, characterized in that a profiling ( 52a ) of at least two distributed over the circumference arranged, as transverse grooves grooves ( 53a ) is formed. Centrifugal pendulum ( 4 ) according to one of claims 1 to 4, characterized in that one of the pendulum elements ( 29b ) or a pendulum roller assigned to a pendulum bearing provided radial profiling ( 52b ) of curved grooves ( 53b . 54b ) with one at the rolling surface ( 50b ) extending in the circumferential direction groove part ( 56b ) and one on a front side ( 55b ) of the pendulum element ( 29b ) or the spherical roller opening groove part ( 57b ) is formed. Centrifugal pendulum ( 4 ) according to claim 5, characterized in that circumferentially curved first grooves ( 53b ) in the rolling direction of the pendulum elements ( 29b ) or spherical rollers first with the on the rolling surface ( 50b ) opening groove part ( 56b ) a rolling surface ( 51 ) of the pendulum element carrier ( 30 ) contacting groove part ( 56b ) with second grooves ( 54b ) with first with the opening on a front side Nutteil ( 57b ) the rolling surface ( 50 ) contacting groove part ( 57b ) alternate. Centrifugal pendulum ( 4 ) according to one of claims 1 to 6, characterized in that a profiling ( 52c ) arranged over the circumference and axially distributed, separate openings ( 53c ) is formed. Hydrodynamic torque converter ( 1 ) with a about an axis of rotation (d) arranged housing ( 14 ) and one in the housing ( 14 ) integrated impeller ( 3 ), the housing ( 14 ) with respect to this rotatably arranged turbine wheel ( 10 ), one between impeller ( 3 ) and turbine wheel ( 10 ) operatively arranged torque converter lockup clutch ( 9 ), optionally a torsional vibration damper ( 13 ) and a centrifugal pendulum ( 4 . 4d ) according to one of claims 1 to 7 receives. Hydrodynamic torque converter ( 1 ) according to claim 8, characterized in that the centrifugal pendulum ( 4 . 4d ) as an output part of the torque converter ( 1 ) is trained. Hydrodynamic torque converter ( 1 ) according to claim 8 or 9, characterized in that the lockup clutch ( 9 ) between outer peripheries of the impeller ( 3 ) and the turbine wheel ( 10 ) is arranged.

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