DE102010034812A1 - Flywheel i.e. two-mass flywheel, has centrifugal force pendulum comprising two pendulum halves, and bolts supported in of supporting plate and comprising rolling body that is designed as bearing outer ring of bearing - Google Patents

Flywheel i.e. two-mass flywheel, has centrifugal force pendulum comprising two pendulum halves, and bolts supported in of supporting plate and comprising rolling body that is designed as bearing outer ring of bearing

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Publication number
DE102010034812A1
DE102010034812A1 DE102010034812A DE102010034812A DE102010034812A1 DE 102010034812 A1 DE102010034812 A1 DE 102010034812A1 DE 102010034812 A DE102010034812 A DE 102010034812A DE 102010034812 A DE102010034812 A DE 102010034812A DE 102010034812 A1 DE102010034812 A1 DE 102010034812A1
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Germany
Prior art keywords
pendulum
characterized
flywheel
halves
according
Prior art date
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Granted
Application number
DE102010034812A
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German (de)
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DE102010034812B4 (en
Inventor
Frank Ferderer
Markus Klinger
Ad Dr. Kooy
Christoph Raber
Tomas Dr. Smetana
Florian Vogel
Marco Wild
Markus Züfle
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Priority to DE102009042074 priority Critical
Priority to DE102009042074.6 priority
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to DE102010034812.0A priority patent/DE102010034812B4/en
Publication of DE102010034812A1 publication Critical patent/DE102010034812A1/en
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Publication of DE102010034812B4 publication Critical patent/DE102010034812B4/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/145Masses mounted with play with respect to driving means thus enabling free movement over a limited range

Abstract

The flywheel has a centrifugal force pendulum (3) comprising two pendulum halves (4a, 4b) that are arranged on two sides of a supporting plate. Bolts (9a, 9b), are movably supported in openings (11a, 11b) of the supporting plate and comprise a rolling body that is designed as a bearing outer ring of a roller bearing. The pendulum halves are designed as parts of a single-piece saddle pendulum that is made of sheet metal by a punching bending process. An insert is designed as a drawn component that is made of steel sheet. Independent claims are also included for the following: (1) a method for manufacturing a saddle pendulum of a flywheel (2) a friction clutch comprising a clutch housing.

Description

  • The invention relates to a flywheel, a friction clutch and a dual mass flywheel according to the preambles of the independent claims.
  • A flywheel with centrifugal pendulums, each comprising two pendulum halves is, for example, from DE 10 2006 028 556 known. The pendulum halves are riveted together in three places. The resulting misalignment of the guide pins can have a negative effect on the load capacity of the centrifugal pendulum. The guide pins have degrees of freedom, they should roll on both the support plate and on the pendulum. However, this does not necessarily have to be ensured in all operating states. The sliding of the guide pins on the carrier plate or on the pendulum halves can lead to avasive wear. The guide pins roll or slide against stamped surfaces under a very high Hertzian pressure of> 3,000 MPa. The relatively poor surface quality of the stamped contact surfaces promotes pitting and reduces the load capacity of the centrifugal pendulum.
  • An object of the present invention is therefore to increase the carrying capacity of the centrifugal pendulum.
  • This problem is solved by a flywheel with at least one centrifugal pendulum, which comprises two pendulum halves, which are arranged on both sides of a support plate and rotatably mounted with at least one guide means which is movably mounted in a guide track of the support plate relative to the support plate, wherein the guide means at least comprises a rolling element.
  • With this measure, in addition to the solution of the above problem, a reduction in the number of parts to be assembled is achieved. This also simplifies the assembly. With the solution according to the invention also an increase in manufacturing accuracy is achieved. With a pendulum motion of the centrifugal pendulum, the friction is reduced, so that less noise occurs. The lower production costs also reduce the production costs.
  • It is preferably provided that the two pendulum halves are part of an integrally manufactured saddle pendulum, which is preferably made of a metal sheet by stamping.
  • It is preferably provided that the rolling element is a bearing outer ring of a roller bearing. The rolling element is preferably arranged on a bolt which is arranged between the pendulum halves. It is preferably provided that the bolt is pressed with the pendulum halves.
  • Rolling elements of the rolling bearing preferably roll on the bolt for connecting the pendulum halves.
  • It is preferably provided that the guide track of the carrier plate is formed by an insert which is arranged in an opening of the carrier plate. Hardness, surface quality and the like of the insert can be defined independently of the values of the support plate.
  • It is preferably provided that the insert is a drawn component made of sheet steel. The roughness of a drawn component is less than that of a stamped surface, which reduces friction and thus wear.
  • It is preferably provided that the insert is hardened at least on the surface which is in contact with the rolling body. This further reduces wear.
  • It is preferably provided that the bearing outer ring is spherically shaped. As a result, angle errors can be compensated.
  • The two pendulum halves were replaced according to the invention by a saddle pendulum. As a result, can be dispensed with the rivet connections between the pendulum halves. The cylindrical guide pins were pressed into the saddle pendulum. On the bolt are full-needle support rollers that guide the pendulum in the carrier plate. The hardened outer ring of the support rollers is slightly convex and thus insensitive to tilting or bolt misalignment. Pulled and hardened inserts were pressed into the punched kidney-shaped holes of the carrier plate. The drawn parts have a very high surface quality and in particular a high bearing ratio compared to stamped surfaces, which has a positive effect on the bearing capacity of the pendulum. In addition, can be dispensed with the heat treatment of the pendulum and the support plate, because there is no direct Hertzian contact with support rollers.
  • The above-mentioned problem is also solved by a saddle pendulum for use on a flywheel according to one of the preceding claims, wherein the two pendulum halves are part of an integrally manufactured saddle pendulum, wherein the saddle pendulum is made of a metal sheet by stamping.
  • The problem mentioned above is also solved by a method for manufacturing a Saddle pendulum, characterized by the process steps
    • - punching a blank
    • - bending into a saddle shape
    • - Punching holes
    • - Assembly of guide means.
  • Known centrifugal pendulums are placed on the flange on the secondary flywheel in a dual-mass flywheel. As a rule, an internal damper must give way. An object of the present invention is therefore to provide a solution in which a centrifugal pendulum can be used in a self-adjusting coupling in addition to an internal damper.
  • This object is achieved by a friction clutch with a clutch housing, wherein in the clutch housing at least one centrifugal pendulum is arranged.
  • Preferably, it is provided that the centrifugal pendulum comprises a pendulum mass, which rolls on spherical rollers, which are supported on the clutch housing.
  • It is preferably provided that a guide cage is arranged on the clutch housing, on which roll the spherical rollers.
  • It is preferably provided that the guide cage has a slot for receiving at least one guide pin of the pendulum mass.
  • It is preferably provided that the guide pins have a bearing bush.
  • It is preferably provided that the spherical rollers have at least one annular groove in which engages a guide rail of the pendulum mass.
  • It is preferably provided that at least one stop limits the pendulum movement of the pendulum mass.
  • It is preferably provided that the stop is a ring which is arranged on a fastening bolt for fastening the guide cage to the clutch cover.
  • With the previously proposed solution, an improvement in the isolation of the vibrations in the drive train is achieved. Due to the solution according to the invention, in the case of a dual-mass flywheel, an internal damper can continue to be used on the flange. The connection of the centrifugal pendulum lies outside and encloses the pendulum mass. The rollers are only subjected to surface pressure. Sliding bushes are used to guide the masses. The pendulum masses consist of manufacturing reasons of several parts, such as 16 parts comprising eight weights, four dowel pins and four plain bearing sleeves. The centrifugal force is supported by a mounting sleeve and the frictional force of the screw. The centrifugal force is distributed between the clutch cover and the secondary flywheel. An inner plate serves as a support for the sensor spring.
  • The individual pendulum masses of a centrifugal pendulum pendulum according to the prior art can, for. B. abut each other during the stop. The hitting the pendulum masses against each other leads to unwanted noise. For this reason, in the prior art, the pendulum masses are designed so that it can not come to beating each other. This is at the expense of space. Another source of noise is striking individual pendulum masses against the flange. To avoid this or to control acoustically, all pendulum masses have a corresponding stop device against the flange, z. B. in the form of special rubber rings.
  • An object of the present invention is therefore to provide a solution that prevents noise when hitting pendulum masses.
  • This object is achieved by a flywheel with several centrifugal pendulums, wherein the ends located in the circumferential direction of the centrifugal pendulum pendulum are shaped so that they leave a roughly equal small gap at a deflection of the centrifugal pendulum.
  • Thanks to the optimized edge contour of the pendulum masses, significant improvements in noise development can be achieved. The optimized contour has a small, constant gap between the pendulum masses. With synchronous movement of the pendulum masses, the small distance between the masses is always the same. The available space can be used completely for pendulum masses. A collision of the individual pendulum masses against each other can cause no noise, since not enough energy can be built up to the clash due to the small gap. Through the small gap, the individual pendulum masses move essentially like a single pendulum mass. The striking of individual pendulum masses against the flange no longer needs to be prevented with a respective stop device but could be controlled with a central stop device. If necessary, even any measures in the stop can be dispensed with. In the case of the stop, the pendulum masses want to fall down by gravity. By the Coupling the masses can do that but not all pendulum masses at the same time. It is fundamentally conceivable that the masses thus cancel their movement and there is no strong impact on the flange and thus no action for stop more is necessary. The outer contour of the pendulum mass is designed so that even with movement of the individual pendulum masses a small constant gap between the masses is present. For a Kreispendelbahngeometrie results for the optimal shape in a borderline case without play for the pendulum mass ends also a circular shape that is related to the pendulum track geometry. Other forms of pendulum geometry are different. The individual pendulum masses can continue to move freely to each other. The space between the individual pendulum masses is limited to a constant value. The ends look essentially circular. The invention allows the use of the available space optimally. In the case of stop and start, the weight force against the centrifugal force is no longer negligible or the dominant force. The individual pendulum masses react differently to the gravitational acceleration due to their current geometric position. This has the consequence that it can come to unintentional striking the pendulum masses together, associated with unwanted noise. The inventive type of pendulum execution does not allow this. Since the pendulum masses can perform virtually no path to each other, the masses move rather synchronously. Only a small gap of the order of about 0.5 mm allows for minimal movement. This low value leads to no noise in the case of clashing of the pendulum.
  • It is preferably provided that the ends of the centrifugal pendulum are rounded in a circle.
  • In dual-mass flywheels according to the prior art, the primary mass is connected to the crankshaft, correspondingly, the flange is connected via further means to the input side of the friction clutch. A disadvantage of this solution is a relatively high space requirement. An object of the present invention is therefore to minimize the space requirement.
  • This object is achieved by a dual-mass flywheel with a primary mass and a flange, which are rotated against each other against the force of a spring, wherein the primary mass at two substantially axially opposite locations of the spring in contact therewith and the flange at two substantially in the radial direction opposite points of the spring is in contact with this, wherein the flange is connectable to a crankshaft and the primary mass carries parts of a friction clutch.
  • In centrifugal pendulum pendulums according to the prior art, the pendulum halves can rub against the carrier plate. An object of the invention is to reduce this.
  • This object is achieved by a flywheel with at least one centrifugal pendulum, which comprises two pendulum halves, which are arranged on both sides of a support plate and connected to at least one connecting means which is movably mounted in a guide track of the support plate, wherein on the connecting means between the two Pendulum halves spacers are arranged.
  • It is preferably provided that two spacers are arranged between the two pendulum halves and a damping ring is arranged between the spacers.
  • It is preferably provided that the two spacers each have a circumferential axial shoulder.
  • It is preferably provided that the two spacers each have a circumferential collar which engages in a stage of the damping ring.
  • The invention is based on the 1 to 13 explained in more detail. Showing:
  • 1 an embodiment of a flywheel according to the invention;
  • 2 a centrifugal pendulum of the embodiment of the 2 ;
  • 3a an enlarged view of parts of the 2 ;
  • 3b an insert;
  • 4 different production stages of a semitrailer
  • 5 a section through a clutch cover;
  • 6 a spatial view of the embodiment according to 5 ;
  • 7 the embodiment of 5 and 6 in a cut;
  • 8th a sketch of a pendulum mass according to the prior art;
  • 9 a sketch of a pendulum mass according to the invention;
  • 10 Sketches of several pendulum masses according to the invention in installation position;
  • 11 a sketch of an embodiment of a dual mass flywheel according to the invention in section;
  • 12 a sketch of another embodiment of a dual mass flywheel according to the invention in section;
  • 13 a partial section through a further embodiment of a flywheel according to the invention;
  • 14 a section through damping ring and spacers in 13 ;
  • 15 a section through alternative spacers;
  • 16 a partial section through a further embodiment of a flywheel according to the invention.
  • The 1 shows a spatial view of an embodiment of a flywheel according to the invention 1 , The flywheel 1 includes a carrier plate 2 , This is substantially disc-shaped and comprises an outer region in which a plurality of centrifugal pendulum pendulum are arranged and an inner portion which has a mounting flange 5 having. With the help of the mounting flange 5 the flywheel is connected for example with a flange, not shown here for further connection to a transmission input shaft. recesses 6 serve to accommodate also not shown springs, which together with the flywheel 1 Part of a dual mass flywheel are.
  • In the outer area of the carrier plate 2 are distributed over the circumference several centrifugal pendulum 3 arranged. To distinguish these with the reference numerals 3a . 3b . 3c and 3d designated. Instead of three centrifugal pendulums as in the embodiment shown here, a larger or smaller number of centrifugal pendulums can be present here. The construction of the centrifugal pendulum is in 2 shown. The centrifugal pendulum 3 includes two pendulum halves 4 , these are for differentiation with the reference numerals 4a and 4b Mistake. The two pendulum halves 4 are by means of pendulum bridges 7 firmly connected. The pendulum halves 4 and the pendulum bridges 7 are integrally, as shown later, made of a sheet metal stamped component. The centrifugal pendulum 3 thus comprises two pendulum halves, which are manufactured in one piece and connected to each other and here as a semitrailer 17 referred to as. The two pendulum halves are arranged on both sides of the carrier plate, the saddle pendulum 17 surrounds the carrier plate 2 so. Except the two pendulum bridges 7 are no further connection means for connecting the two pendulum halves 4a . 4b intended.
  • In the two pendulum halves 4a . 4b are each two holes 8a . 8b introduced, the holes 8a and 8b So are each in both the pendulum half 4a as well as in the pendulum half 4b arranged so that they form a total of one through hole. In the holes 8a and 8b are bolts 9 Pressed, each a rolling bearing 10 wear. In 1 are the two pendulum halves 4a . 4b for the centrifugal pendulum 3a not shown, so the arrangement of the bolts 9 and rolling bearings 10 can be seen. Bolts 9a . 9b penetrate openings 11a respectively. 11b in the carrier plate 2 so that the rolling bearings 10a and 10b each with the surface 12a respectively. 12b are in contact. The 3a shows the opening 11b in 2 in an enlarged view. The 3b shows the insert 15 in 3a , In the 3 and 4 were the indices a and b, as in 1 and 2 used, suppressed. The rolling bearings 10 are needle roller bearings and include a bearing outer ring 13 as well as needles 14 that are directly on the bolt 9 roll. The bearing outer ring 13 is thus rotatable relative to the bolt 9 stored. The surface 14 of the bearing outer ring 13 can on the surface 12 the opening 11 roll.
  • In the openings 11 are each inserts 15a . 15b pressed. The inner surface of the inserts 15 forms the surface 12 the openings 11 on which the surface 14 of the bearing outer ring 13 rolls. The stakes 15 are each drawn and optionally surface-hardened sheet metal parts in correspondingly shaped openings of the support plate 2 be pressed in, so that the inner surface of the openings 11 through the inner surface of the inserts 15 is formed. By manufacturing the inserts 15 as a deep-drawn part whose surface is comparatively less rough, at least compared to a stamped component such as the carrier plate 2 , so here when rolling the bearing outer rings 13 correspondingly little wear occurs. Due to the rather large diameter of the bearing outer rings 13 is also the surface pressure on the inner surface 12 the openings 11 compared to solutions according to the prior art, comparatively low.
  • In the carrier plate 2 Eats between the openings 11a . 11b a recess 16 introduced, which is a striking of pendulum bridges 7 to the carrier plate 2 should prevent.
  • The 4 shows different production stages of the semitrailer 17 , In a first Production step according to 4a ) becomes the contour of a settlement of the semitrailer 17 punched. Settlement insofar as that the pendulum bridges 7 unwound in one plane, whereby the two pendulum halves 4a . 4b lie in a parallel plane. In a next step according to 4b ) is the blank according to 4a ) bent into the saddle shape. In a further step according to 4c ) are in a pendulum half the holes 8th stamped or drilled, in a further step according to 4d ), the holes are drilled or punched in the other pendulum half.
  • 5 shows a section through a clutch cover of an embodiment of a friction clutch according to the invention. Shown by the friction clutch is only a clutch cover 18 , With axial direction is here as in the following and preceding text, the axial direction with respect to the axis of rotation of the clutch cover 18 meant, this reference also applies to the designation radial direction and circumferential direction. For example, the axial direction protrudes in 5 out of the drawing plane. According to the invention is / are in the clutch cover 18 integrated one or more centrifugal pendulum. 5 shows a schematic diagram. The clutch cover 18 has a bag 19 on, in a guide cage 20 is arranged. With respect to the axis of rotation of the clutch cover 18 radially inner side of the guide cage 20 are two spherical rollers 21a and 21b arranged on which a pendulum mass 22 can roll and so a relative rotation and displacement relative to the clutch cover 18 can perform. The basic function for vibration damping such a pendulum mass is, for example, from the DE 10 2006 028 556 known and will not be described here.
  • The 6 shows the spatial view of the embodiment according to 5 from a view from radially outside to the guide cage 20 , The guide cage 20 has a substantially U-shaped cross section, and includes two side surfaces 23a and 23b through a connection back 24 connected to each other. The connection back 24 extends only over part of the radial circumference of the side surfaces 23 , At their radial outer areas have the side surfaces 23 each drilling 25a . 25b on, through the fastening bolts 26a and 26b are guided. The fastening bolts 26a . 26b pierced each receiving holes in the clutch cover 18 , With the help of the fastening bolts 26 becomes the guide cage 20 on the clutch cover 18 attached. The fastening bolts 26a . 26b wear rubber rings 27a . 27b , on the one hand the axial positioning of the guide cage 20 opposite the clutch cover 18 serve, on the other hand, as explained later, stop elements for limiting the pendulum path of the pendulum mass 22 form. The side surfaces 23 each have backdrops 79 on, in the guide pins 28 that with the attachment of the pendulum mass 22 connected, intervene. The guide pins 28 together with the scenes 79 form a guide for the pendulum mass 22 and show the pendulum mass on a pendulum.
  • The 7 shows the embodiment of the 5 and 6 in a cut. To recognize is the guide cage 20 on which the pendulum rollers 21 roll. The pendulum mass 22 relies on the spherical rollers 21 from. The pendulum rollers 21 are in radially outwardly convex formed bulges 29 arranged. Radial on the inside with respect to the clutch cover 18 is an apron 30 arranged.
  • The pendulum mass 22 is made of a sheet pile consisting of individual sheets 22.1 . 22.2 . 22.3 educated. Between the individual sheets 22.1 and 22.2 as well as between the individual sheets 22.2 and 22.3 are each intermediate plates 31a and 31b arranged. The intermediate plates have at least in the contact area with the spherical rollers 21 a contour that exceeds that of the individual sheets 21.1 . 21.2 . 21.3 the sheet pile protrudes so that these circumferential raised ledges 32 form. The strips 32 each grab in Ringnute 33 of the spherical rollers and thus form a guide in the axial direction for the spherical rollers 21 , The guide pins 28 At the same time form a connection of the individual sheets of the laminated core of the pendulum mass 22 , In addition, the individual sheets are with rivets 34 riveted together.
  • The 8th shows a sketch of a pendulum mass according to the prior art. Such pendulum mass is for example in the DE 10 2006 028 556 in this respect, reference is made in full to the representation therein. The pendulum mass is around a pivot point 34 rotatably suspended from the support plate, not shown. At their two with respect to the fulcrum 34 in the circumferential direction ends 36 she is to the centrifugal pendulum 3 each flattened, thus has substantially straight cut ends. Accordingly, in the prior art, see, for. B. the previously cited DE 10 2006 028 556 , provided that the pendulum have a correspondingly large distance and also ensure slings ensure that the pendulum as possible can not hit each other.
  • According to the invention is now on the one hand, a contour of the circumferentially located ends of the centrifugal pendulum 3 as in 9 intended. Here the ends are rounded off, for example by giving them a radius with respect to a center point 37 exhibit. On the other hand, it is provided that the distance of the individual centrifugal pendulum in the circumferential direction is reduced from each other, so that only a small gap between them remains. This is in 10a shown. With deflection of the individual centrifugal pendulum 3a . 3b . 3c . 3d the gap remains approximately constant, this is in 10b shown. This will cause a hitting the individual centrifugal pendulum 3 avoided against each other during operation. When approach and departure, so if the influence of gravity outweighs, the pendulum can still hit each other. The lower gap between the centrifugal pendulums, which is smaller in each position of the pendulum, ensures that only a small amount of noise develops due to this collision. The optimal contour according to the embodiment of 9 and 10 has a small, constant gap between the pendulum masses. With synchronous movement of the pendulum masses, the small distance between the masses is always the same. Experienced bore can be used completely for pendulum masses. A collision of the individual pendulum masses against each other causes no noise, since not enough energy can be built up to the clash due to the small gap. Through the small gap, the individual pendulum masses move essentially like a single pendulum mass. The striking of individual pendulum mass against the flange must be prevented not only with a respective stop device, but could be controlled with a central stop device. If necessary, even any measure in the stop can be dispensed with. In the case of a stop, the pendulum masses want to fall down. By coupling the masses, however, all pendulum masses can not do that at the same time. It is basically conceivable that the masses thus cancel in their movement and there is no strong impact on the flange and thus no action for stop is necessary.
  • For a circular path of the pendulum track geometry results for the optimal shape, so a borderline case without play, for the pendulum mass ends also a circular shape, which is in a fixed relationship to the pendulum track geometry. For other pendulum track geometries correspondingly different shapes result. The ends of the pendulum masses look essentially circular.
  • The 11 and 12 show exemplary embodiments of inventive dual-mass flywheels 40 on average. The dual mass flywheel 40 includes a primary mass 41 that have bow springs 42 with a flange 43 connected is. In a relative rotation of the primary mass 41 opposite the flange 43 becomes the bow spring 42 or become the multiple bow springs 42 curious, so that a relative rotation of the primary mass 41 opposite the flange 43 given against the force of a spring accumulator. The flange 43 is stuck with a crankshaft 44 connected. The primary mass 41 is fixed to the input side of the friction clutch 45 connected. The input side of the friction clutch 45 is here represented by a counterfoil 46 that is solid with the primary mass 41 connected is. In this respect forms the primary mass 41 with the counter covering 46 the counter-pressure plate of the friction clutch 45 , A printing plate 47 with a friction lining 48 is fixed to the housing by a housing 49 mounted plate spring 50 against the counter-pressure plate consisting of primary mass 41 and counter covering 46 pressed. The plate spring is on a disc spring bearing 51 fixed to the housing with respect to the coupling housing 51 stored. The bias of the diaphragm spring 50 is chosen so that the pressure plate 47 in the direction of the primary mass 41 is pressed. Will be an inner flange 52 the plate spring 50 for example, by means of a release bearing in the direction of the primary mass 41 pressed, the radially outer portion of the plate spring is moved in the opposite direction, so that the pressure plate 47 is relieved. A clutch disc 53 is between the counterfoil 46 and the friction lining 48 arranged. Will the pressure plate 47 pressed on the counter-pressure plate, so is a frictional connection between the counter-covering 46 or friction lining 48 and the clutch disc 53 made so that rotation with transmission is possible. The clutch disc 53 is about a washer 54 , a disc flange 55 by means of an axial toothing 57 with a transmission input shaft 56 connected. The individual discs are riveted together. A paragraph 58 the crankshaft 56 carries a rolling bearing 59 , which may also be a plain bearing, with an inner flange 60 that stuck to the flange 43 is, is mounted radially. In this way is also a centering of the transmission input shaft 56 opposite the crankshaft 44 given. The primary mass 41 is in its radially inner region with a bearing ring 61 provided, opposite the inner flange 60 is slidably mounted. In addition, friction agents 62 be provided, which provides additional friction damping at a relative rotation of the primary mass 41 opposite the flange 43 produce. The primary mass 41 is additionally with Masseringen 63 provided that increase their mass. The coupling housing 49 is by means of screws 64 with the primary mass 41 screwed. A friction ring 69 is fixed to the flange 43 connected and is in contact with a friction disc 70 that stuck with the primary mass 41 connected is. In a relative rotation of the primary mass 41 opposite the flange 43 slide the friction ring 69 and the friction disc 70 with dry friction on each other and thus produce a further damping.
  • 12 shows an alternative embodiment of a dual mass flywheel according to the invention in section. Across from 11 the same parts are not described again here and identically labeled. In contrast to the embodiment of 11 here the storage takes place such that a rolling bearing 65 , for example, a Ball bearing, with an annular approach 66 that stuck to the flange 43 is connected. The determination can for example by means of a spacer sleeve 67 and a circlip 68 respectively.
  • 13 shows an embodiment of a flywheel 1 in which the pendulum halves 4a . 4b through rivets 71 connected to each other. The rivet has a thickening 72 , The rivet 71 wears two spacers 73a . 73b between the carrier plate 2 and the respective pendulum halves 4a . 4b are arranged. The spacers 73a . 73b have a bore with an inner diameter corresponding to the outer diameter of the thickening 72 on. Between the spacers 73a . 73b is a damping ring 74 arranged. The spacers 73 For example, they are made of plastic and prevent direct contact between the pendulum halves 4a . 4b and the carrier plate 2 , Instead of a three-piece construction spacers 73a , Damping ring 74 , Spacers 73b ( 14 ) can also be a two-piece design according to 15 be used. Here are the spacers 73 each a circumferential axial shoulder 75 on. The two circumferential heels complement each other to form a damping ring.
  • 16 shows a further embodiment in which the spacers 73a . 73b a wraparound collar 76 have in one step 77 a stepped bore in the damping ring 74 intervenes.
  • LIST OF REFERENCE NUMBERS
  • 1
    flywheel
    2
    support plate
    3
    centrifugal pendulum
    4
    pendulum half
    5
    mounting flange
    6
    recess
    7
    pendulum
    8th
    drilling
    9
    bolt
    10
    roller bearing
    11
    opening
    12
    surface
    13
    Bearing outer ring
    14
    surface
    15
    commitment
    16
    recess
    17
    saddle pendulum
    18
    clutch cover
    19
    bag
    20
    guide cage
    21
    Spherical roller
    22
    pendulum mass
    23
    side surface
    24
    connection back
    25
    drilling
    26
    mounting bolts
    27
    rubber rings
    28
    guide pins
    29
    bulge
    30
    mudguard
    31
    intermediate plate
    32
    strip
    33
    annular groove
    34
    rivet
    35
    pivot point
    36
    The End
    37
    Focus
    40
    Dual Mass Flywheel
    41
    primary mass
    42
    bow spring
    43
    flange
    44
    crankshaft
    45
    friction clutch
    46
    mating coating
    47
    printing plate
    48
    friction lining
    49
    clutch housing
    50
    Belleville spring
    51
    Belleville spring camp
    52
    inner flange
    53
    clutch disc
    54
    washer
    55
    disk flange
    56
    Transmission input shaft
    57
    axial toothing
    58
    paragraph
    59
    roller bearing
    60
    inner flange
    61
    bearing ring
    62
    friction means
    63
    ground ring
    64
    screw
    65
    roller bearing
    66
    annular approach
    67
    Stand Off
    68
    circlip
    69
    friction ring
    70
    friction
    71
    rivet
    72
    thickening
    73
    spacer
    74
    damping ring
    75
    axial heel
    76
    circumferential collar
    77
    step
    79
    scenery
  • 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
    • DE 102006028556 [0002, 0062, 0066, 0066]

Claims (28)

  1. Flywheel ( 1 ) with at least one centrifugal pendulum ( 3 ), the two pendulum halves ( 4a . 4b ), which on both sides of a support plate ( 2 ) are arranged and with at least one guide means ( 9 . 10 ), in a guideway ( 11 ) of the carrier plate ( 2 ) is movably mounted, rotatable relative to the carrier plate ( 2 ) is mounted, characterized in that the guide means at least one rolling element ( 10 . 13 ).
  2. Flywheel according to claim 1, characterized in that the two pendulum halves ( 4a . 4b ) Part of a one-piece semi-trailer ( 17 ) are.
  3. Flywheel according to claim 2, characterized in that the saddle pendulum ( 17 ) is made from a sheet by stamping.
  4. Flywheel according to one of claims 1 to 3, characterized in that the rolling body is a bearing outer ring ( 13 ) of a rolling bearing ( 10 ).
  5. Flywheel according to one of claims 1 to 4, characterized in that the rolling body ( 13 ) on a bolt ( 9 ) suspended between the pendulum halves ( 4a . 4b ) is arranged.
  6. Flywheel according to claim 5, characterized in that the bolt ( 9 ) with the pendulum halves ( 4a . 4b ) is compressed.
  7. Flywheel according to one of claims 1 to 6, characterized in that rolling elements of the rolling bearing ( 10 ) on the bolt ( 9 ) for connecting the pendulum halves ( 4a . 4b ).
  8. Flywheel according to one of claims 1 to 7, characterized in that the guideway of the carrier plate ( 2 ) through an insert ( 15 ), which in an opening of the carrier plate ( 2 ) is formed.
  9. Flywheel according to claim 8, characterized in that the insert ( 15 ) is a drawn component made of sheet steel.
  10. Flywheel according to claim 9, characterized in that the insert ( 15 ) at least on the surface, which with the rolling body ( 13 ) is in contact, is cured.
  11. Flywheel according to one of claims 4 to 10, characterized in that the bearing outer ring ( 13 ) is spherically shaped.
  12. Saddle pendulum ( 17 ) for use on a flywheel ( 1 ) according to one of the preceding claims, characterized in that the two pendulum halves ( 4a . 4b ) Part of a one-piece semi-trailer ( 17 ), the saddle pendulum ( 17 ) is made from a sheet by stamping.
  13. Method for producing a saddle pendulum ( 17 ) for use on a flywheel according to one of claims 1 to 11, characterized by the method steps - punching a blank - bending into a saddle shape - drilling holes - assembly of guide means
  14. Friction clutch with a clutch housing ( 49 ), characterized in that in the coupling housing ( 49 ) at least one centrifugal pendulum ( 3 ) is arranged.
  15. Friction clutch according to claim 14, characterized in that the centrifugal pendulum pendulum mass ( 22 ) mounted on spherical rollers ( 21 ) located on the coupling housing ( 49 ), rolls off.
  16. Friction clutch according to claim 15, characterized in that on the clutch housing ( 49 ) a guide cage ( 20 ) is arranged, on which the spherical rollers ( 21 ).
  17. Friction clutch according to claim 16, characterized in that the guide cage ( 20 ) a backdrop ( 79 ) for receiving at least one guide pin ( 28 ) of the pendulum mass ( 22 ) having.
  18. Friction clutch according to claim 17, characterized in that the guide pins ( 28 ) have a bearing bush.
  19. Friction clutch according to one of claims 14 to 18, characterized in that the spherical rollers ( 21 ) have at least one annular groove in which a guide strip ( 32 ) of the pendulum mass ( 22 ) intervenes.
  20. Friction clutch according to one of claims 14 to 19, characterized in that at least one stop the pendulum movement of the pendulum mass ( 22 ) limited.
  21. Friction clutch according to claim 20, characterized in that the stop is a ring ( 27 ), which is attached to a fastening bolt ( 26 ) for fixing the guide cage ( 20 ) on the coupling housing ( 49 ) is arranged.
  22. Flywheel with several centrifugal pendulums ( 3 ), characterized in that located in the circumferential direction of the centrifugal pendulum ends ( 36 ) are formed so that these at a deflection of the Centrifugal pendulum leave a roughly equal small gap.
  23. Flywheel according to claim 22, characterized in that the ends ( 36 ) of the centrifugal pendulum are rounded in a circle.
  24. Dual mass flywheel with a primary mass ( 41 ) and a flange ( 43 ) against the force of a spring ( 42 ) are rotatable against each other, wherein the primary mass ( 41 ) are in contact with the spring at two substantially axially opposite points of the spring and the flange ( 43 ) at two substantially radially opposite points of the spring ( 42 ) is in contact with this, characterized in that the flange ( 43 ) is connectable to a crankshaft and the primary mass ( 41 ) Carries parts of a friction clutch.
  25. Flywheel with at least one centrifugal pendulum, the two pendulum halves ( 4a . 4b ), which on both sides of a support plate ( 2 ) are arranged and with at least one connecting means, which in a guideway of the carrier plate ( 2 ) are movably mounted, are interconnected, characterized in that on the connecting means between the two pendulum halves ( 4a . 4b ) Spacers ( 73 ) are arranged.
  26. Flywheel according to claim 25, characterized in that between the two pendulum halves ( 4a . 4b ) two spacers ( 73a . 73b ) are arranged and between the spacers ( 73a . 73b ) a damping ring ( 74 ) is arranged.
  27. Flywheel according to claim 26, characterized in that the two spacers ( 73a . 73b ) each have a circumferential axial shoulder ( 75 ) exhibit.
  28. Flywheel according to claim 27, characterized in that the two spacers ( 73a . 73b ) each have a circumferential collar ( 76 ), which enters a stage ( 77 ) of the damping ring ( 74 ) intervenes.
DE102010034812.0A 2009-09-17 2010-08-19 Flywheel and friction clutch Active DE102010034812B4 (en)

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DE102009042074 2009-09-17
DE102009042074.6 2009-09-17
DE102010034812.0A DE102010034812B4 (en) 2009-09-17 2010-08-19 Flywheel and friction clutch

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Application Number Priority Date Filing Date Title
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DE102010034812B4 DE102010034812B4 (en) 2018-06-21

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Cited By (25)

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WO2012150401A1 (en) * 2011-05-04 2012-11-08 Valeo Embrayages Torsion damping device comprising pendular flyweights mounted on a phase washer
WO2012171515A1 (en) * 2011-06-14 2012-12-20 Schaeffler Technologies AG & Co. KG Centrifugal force pendulum
DE102012212895A1 (en) 2011-08-18 2013-02-21 Schaeffler Technologies AG & Co. KG Centrifugal force pendulum device for power train of internal combustion engine-driven motor car, has pendulum mass provided with mass portions spaced from each other, where mass portions are interconnected by carrier plate
DE102012213124A1 (en) 2011-08-18 2013-02-21 Schaeffler Technologies AG & Co. KG Centrifugal pendulum device, particularly for drive train of internal combustion engine driven motor vehicle, comprises pendulum mass support element rotating around axis of rotation, and pendulum mass formed with turned sheet metal plate
WO2013034125A1 (en) 2011-09-09 2013-03-14 Schaeffler Technologies AG & Co. KG Centrifugal pendulum and clutch disc having the latter
EP2667050A1 (en) * 2012-05-23 2013-11-27 Valeo Embrayages Torque transmission device for a motor vehicle
EP2719920A1 (en) * 2012-10-11 2014-04-16 Valeo Embrayages Dual mass flywheel including a pendulum damper
WO2014096624A1 (en) 2012-12-20 2014-06-26 Valeo Embrayages Pendular damping device
WO2014096614A1 (en) * 2012-12-21 2014-06-26 Valeo Embrayages Device for absorbing vibrations
WO2014096612A1 (en) * 2012-12-21 2014-06-26 Valeo Embrayages Vibration absorbing device
FR3000158A1 (en) * 2012-12-21 2014-06-27 Valeo Embrayages Vibration absorbing device for use in transmission device such as friction clutch, of car, has inner rolling body and/or one of outer rolling bodies and/or support and/or weight comprising stops to limit axial movement of rolling bodies
FR3000160A1 (en) * 2012-12-21 2014-06-27 Valeo Embrayages Vibration absorbing device for use in transmission device such as friction clutch, of car, has counterweight contained in virtual enclosure, where counterweight rests on set of contours of window, and projects axially from mounting
FR3000159A1 (en) * 2012-12-21 2014-06-27 Valeo Embrayages Vibration absorbing device for use in transmission device such as friction clutch, of car, has inner rolling body and/or one of outer rolling bodies and/or support and/or weight comprising stops to limit axial movement of rolling bodies
FR3000162A1 (en) * 2012-12-21 2014-06-27 Valeo Embrayages Vibration absorbing device for use in transmission device such as friction clutch, of car, has counterweight contained in virtual enclosure, where counterweight rests on set of contours of window, and projects axially from mounting
FR3000161A1 (en) * 2012-12-21 2014-06-27 Valeo Embrayages Vibration absorbing device for use in transmission device such as friction clutch, of car, has counterweight contained in virtual enclosure, where counterweight rests on set of contours of window, and projects axially from mounting
CN103975145A (en) * 2011-12-05 2014-08-06 舍弗勒技术有限两合公司 Drive train
DE102014110233A1 (en) 2013-07-19 2015-01-22 Valeo Embrayages Damping system of the pendulum oscillator type
US20150101450A1 (en) * 2011-11-28 2015-04-16 Schaeffler Technologies Gmbh & Co. Kg Centrifugal force pendulum
US20150167779A1 (en) * 2012-08-27 2015-06-18 Bayerische Motoren Werke Aktiengesellschaft Centrifugal Pendulum
WO2015192846A1 (en) * 2014-06-18 2015-12-23 Schaeffler Technologies AG & Co. KG Centrifugal pendulum
CN105605151A (en) * 2014-11-18 2016-05-25 舍弗勒技术股份两合公司 Single-mass flywheel with centrifugal pendulum
FR3032249A1 (en) * 2015-01-30 2016-08-05 Valeo Embrayages Torsion oscillation damping device
FR3049032A1 (en) * 2016-03-21 2017-09-22 Valeo Embrayages Pendular damping device
DE102011086526B4 (en) 2010-12-15 2018-08-02 Schaeffler Technologies AG & Co. KG A torsional vibration absorber device and a torque transmission device for a motor vehicle
EP3158224B1 (en) 2014-06-18 2018-11-28 Schaeffler Technologies AG & Co. KG Torsional vibration damper

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DE102011086526B4 (en) 2010-12-15 2018-08-02 Schaeffler Technologies AG & Co. KG A torsional vibration absorber device and a torque transmission device for a motor vehicle
WO2012150401A1 (en) * 2011-05-04 2012-11-08 Valeo Embrayages Torsion damping device comprising pendular flyweights mounted on a phase washer
EP2705273B1 (en) 2011-05-04 2019-03-27 Valeo Embrayages Torsion damping device comprising pendular flyweights mounted on a phase washer
FR2974870A1 (en) * 2011-05-04 2012-11-09 Valeo Embrayages Torsion damping device having pendulum masselots mounted on a phasing washer
WO2012171515A1 (en) * 2011-06-14 2012-12-20 Schaeffler Technologies AG & Co. KG Centrifugal force pendulum
CN103620259A (en) * 2011-06-14 2014-03-05 舍弗勒技术股份两合公司 Centrifugal force pendulum
CN103620259B (en) * 2011-06-14 2015-12-02 舍弗勒技术股份两合公司 centrifugal force pendulum
DE102012212895A1 (en) 2011-08-18 2013-02-21 Schaeffler Technologies AG & Co. KG Centrifugal force pendulum device for power train of internal combustion engine-driven motor car, has pendulum mass provided with mass portions spaced from each other, where mass portions are interconnected by carrier plate
DE102012213124A1 (en) 2011-08-18 2013-02-21 Schaeffler Technologies AG & Co. KG Centrifugal pendulum device, particularly for drive train of internal combustion engine driven motor vehicle, comprises pendulum mass support element rotating around axis of rotation, and pendulum mass formed with turned sheet metal plate
DE102012214813A1 (en) 2011-09-09 2013-03-14 Schaeffler Technologies AG & Co. KG Centrifugal pendulum and clutch disc with this
WO2013034125A1 (en) 2011-09-09 2013-03-14 Schaeffler Technologies AG & Co. KG Centrifugal pendulum and clutch disc having the latter
US9574615B2 (en) 2011-09-09 2017-02-21 Schaeffler Technologies AG & Co. KG Centrifugal pendulum and clutch disc having the latter
US20150101450A1 (en) * 2011-11-28 2015-04-16 Schaeffler Technologies Gmbh & Co. Kg Centrifugal force pendulum
US9631696B2 (en) * 2011-11-28 2017-04-25 Schaeffler Technologies AG & Co. KG Centrifugal force pendulum
CN103975145A (en) * 2011-12-05 2014-08-06 舍弗勒技术有限两合公司 Drive train
US20140298952A1 (en) * 2011-12-05 2014-10-09 Schaeffler Technologies Gmbh & Co. Kg Drive train
EP2667050A1 (en) * 2012-05-23 2013-11-27 Valeo Embrayages Torque transmission device for a motor vehicle
FR2991017A1 (en) * 2012-05-23 2013-11-29 Valeo Embrayages Torque transmission device for a motor vehicle
US20150167779A1 (en) * 2012-08-27 2015-06-18 Bayerische Motoren Werke Aktiengesellschaft Centrifugal Pendulum
US9915317B2 (en) * 2012-08-27 2018-03-13 Bayerische Motoren Werke Aktiengesellschaft Centrifugal pendulum
EP2719920A1 (en) * 2012-10-11 2014-04-16 Valeo Embrayages Dual mass flywheel including a pendulum damper
FR2996893A1 (en) * 2012-10-11 2014-04-18 Valeo Embrayages Double flywheel damper equipped with a pendular damping device
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WO2014096612A1 (en) * 2012-12-21 2014-06-26 Valeo Embrayages Vibration absorbing device
FR3000162A1 (en) * 2012-12-21 2014-06-27 Valeo Embrayages Vibration absorbing device for use in transmission device such as friction clutch, of car, has counterweight contained in virtual enclosure, where counterweight rests on set of contours of window, and projects axially from mounting
FR3000159A1 (en) * 2012-12-21 2014-06-27 Valeo Embrayages Vibration absorbing device for use in transmission device such as friction clutch, of car, has inner rolling body and/or one of outer rolling bodies and/or support and/or weight comprising stops to limit axial movement of rolling bodies
FR3000160A1 (en) * 2012-12-21 2014-06-27 Valeo Embrayages Vibration absorbing device for use in transmission device such as friction clutch, of car, has counterweight contained in virtual enclosure, where counterweight rests on set of contours of window, and projects axially from mounting
WO2014096614A1 (en) * 2012-12-21 2014-06-26 Valeo Embrayages Device for absorbing vibrations
FR3000158A1 (en) * 2012-12-21 2014-06-27 Valeo Embrayages Vibration absorbing device for use in transmission device such as friction clutch, of car, has inner rolling body and/or one of outer rolling bodies and/or support and/or weight comprising stops to limit axial movement of rolling bodies
FR3000161A1 (en) * 2012-12-21 2014-06-27 Valeo Embrayages Vibration absorbing device for use in transmission device such as friction clutch, of car, has counterweight contained in virtual enclosure, where counterweight rests on set of contours of window, and projects axially from mounting
DE102014110233A1 (en) 2013-07-19 2015-01-22 Valeo Embrayages Damping system of the pendulum oscillator type
EP3158225B1 (en) 2014-06-18 2018-11-28 Schaeffler Technologies AG & Co. KG Centrifugal pendulum
CN106461012B (en) * 2014-06-18 2019-07-09 舍弗勒技术股份两合公司 Centrifugal force pendulum
WO2015192846A1 (en) * 2014-06-18 2015-12-23 Schaeffler Technologies AG & Co. KG Centrifugal pendulum
EP3158224B1 (en) 2014-06-18 2018-11-28 Schaeffler Technologies AG & Co. KG Torsional vibration damper
CN105605151A (en) * 2014-11-18 2016-05-25 舍弗勒技术股份两合公司 Single-mass flywheel with centrifugal pendulum
FR3032249A1 (en) * 2015-01-30 2016-08-05 Valeo Embrayages Torsion oscillation damping device
FR3049032A1 (en) * 2016-03-21 2017-09-22 Valeo Embrayages Pendular damping device
EP3222877A1 (en) * 2016-03-21 2017-09-27 Valeo Embrayages Pendulum damping device

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