EP3146233A1 - Amortisseur de vibrations de torsion - Google Patents

Amortisseur de vibrations de torsion

Info

Publication number
EP3146233A1
EP3146233A1 EP15725491.3A EP15725491A EP3146233A1 EP 3146233 A1 EP3146233 A1 EP 3146233A1 EP 15725491 A EP15725491 A EP 15725491A EP 3146233 A1 EP3146233 A1 EP 3146233A1
Authority
EP
European Patent Office
Prior art keywords
inner ring
bearing
torsional vibration
vibration damper
rolling
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP15725491.3A
Other languages
German (de)
English (en)
Inventor
Hartmut Mende
Ralf Edl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP3146233A1 publication Critical patent/EP3146233A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/13164—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses characterised by the supporting arrangement of the damper unit
    • F16F15/13171—Bearing arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F16C19/166—Four-point-contact ball bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft

Definitions

  • the invention relates to a torsional vibration damper, in particular a dual mass flywheel, comprising an input part and an output part with a common axis of rotation about which the input part and the output part together rotatable and rotatable by means of a rolling bearing limited relative to each other, wherein the rolling bearing an outer ring, an inner ring and a plurality Has arranged between the outer ring and the inner ring rolling elements.
  • German patent application with the file number DE 10 2013 204 233.7 is a dual mass flywheel with two rotatable about a rotational axis rotatable flywheels and arranged between them, an axially fixed pivot bearing of the flywheels providing rolling bearings with an inner ring and an outer ring and on Running surfaces of this rolling rolling elements known in which a degree of filling of the rolling elements is equal to greater than 180 ° and the rolling elements in the circumferential direction against each other are displaced.
  • a degree of filling is understood here as meaning the angle which the rolling elements occupy in contact with one another over the circumference. So that a degree of filling greater than or equal to 180 ° can be achieved, the outer ring of the rolling bearing is formed divided.
  • a mounting method for rolling bearings with an undivided inner ring, an undivided outer ring and rolling in rolling grooves of inner ring and outer ring rolling elements It is provided that in a first assembly step, the rolling elements are placed adjacent to each other in the outer ring. Subsequently, the inner ring is inserted in an eccentric position in the outer ring.
  • the maximum number of rolling elements of the rolling bearing results from the fact that the inner ring can only be used eccentrically when the rolling elements abut each other only in a limited portion of the circumference, while no rolling elements are arranged in an opposite region, so that the inner ring in Direction of this rolling body-free area is eccentrically displaced.
  • the inner ring is brought into a concentric position relative to the outer ring.
  • the rolling elements are then distributed equidistantly over the circumference and fixed with a cage.
  • a torsional vibration damper is to be provided with a rolling bearing with the highest possible number of rolling elements.
  • a torsional vibration damper is to be provided with a rolling bearing with the highest possible degree of filling.
  • a torsional vibration damper is to be provided with an optimized in terms of reliability rolling bearings with which an input part and an output part of the torsional vibration damper can be mounted rotatably limited relative to each other.
  • a torsional vibration damper is to be provided with a roller bearing, which avoids bearing failures by a cage failure.
  • a torsional vibration damper is to be provided with a rolling bearing, which is constructed without a cage.
  • a torsional vibration damper is to be provided with a sealed rolling bearing, from a
  • Lubricant can not escape from the interior of the bearing.
  • a torsional vibration damper in particular a dual-mass flywheel, comprising an input part and an output part with a common axis of rotation about which the input part and the output part together rotatable and rotatable by means of a rolling bearing limited relative to each other, wherein the rolling bearing an outer ring, a Inner ring and a plurality of arranged between the outer ring and the inner ring rolling elements, wherein the inner ring has at least two structurally separately produced inner ring parts.
  • the torsional vibration damper may be a dual mass flywheel.
  • An example of a dual-mass flywheel is disclosed in DE 42 39 770 C2.
  • the torsional vibration damper may be an accessory drive damper, for example, for a starter of an internal combustion engine.
  • the torsional vibration damper may be a clutch damper.
  • the torsional vibration damper can be used for arrangement in a drive train of a motor vehicle.
  • the drive train may include an internal combustion engine.
  • the powertrain may include a friction clutch device.
  • the drive train may have a transmission.
  • the drive train may have at least one drivable wheel.
  • the torsional vibration damper can serve for the arrangement between the internal combustion engine and the friction clutch device.
  • the torsional vibration damper can serve to reduce torsional vibrations, which are excited by periodic processes, in particular in the internal combustion engine.
  • the input part can be connected to the drive-side connection, in particular with an internal combustion engine, serve.
  • the output part can serve for the output-side connection, in particular with a friction clutch device.
  • the terms "input part” and “output part” are based on a, in particular emanating from an internal combustion engine, power flow direction.
  • the powertrain may be a hybrid powertrain for a motor vehicle.
  • Powertrain can be a parallel hybrid powertrain.
  • the powertrain may be a full hybrid powertrain.
  • the powertrain may include a first energy converter and a second energy converter.
  • the first energy converter can be used to convert chemical energy into kinetic energy.
  • An internal combustion engine may be the first energy converter.
  • the internal combustion engine may be operable with a hydrocarbon such as gasoline, diesel, liquefied petroleum gas (LPG, GPL), compressed natural gas (CNG), or liquefied natural gas (LNG).
  • the internal combustion engine can be operated with hydrogen.
  • a first energy store may be provided.
  • the first energy store may be a fluid tank.
  • the second energy converter can be used to convert electrical energy into kinetic energy.
  • the electric machine may be the second energy converter.
  • the electric machine can be operated as a motor.
  • the electric machine can be operated as a generator.
  • the electric machine can structurally combine a motor and a generator.
  • a second energy store may be provided.
  • the second energy store may be an electrical energy store.
  • the second energy store may be an accumulator.
  • the first energy converter and / or the second energy converter can serve for the selective or parallel drive of the motor vehicle.
  • a spring-damper device can be effective.
  • the spring-damper device may comprise a friction device.
  • the spring-damper device may comprise a spring device.
  • the spring device may have at least one energy store.
  • the at least one energy store can have at least one spring.
  • the at least one spring may be a compression spring.
  • the at least one spring may be a coil spring.
  • the at least one spring may be a bow spring.
  • the at least one energy store may have a first spring and a second spring.
  • the first spring and the second spring may be arranged nested one inside the other.
  • the at least one energy store can be effective in the thrust direction and / or in the pulling direction.
  • a thrust direction is directed toward the engine Power flow direction.
  • a pulling direction is a power flow direction emanating from the internal combustion engine.
  • the rolling elements can first be positioned within the outer ring and then the inner ring of the structurally separately produced inner ring parts are assembled. Due to the use of a split inner ring, the inner ring parts can be assembled in one of the last assembly steps to accommodate a large number of balls. As a result, fill levels significantly greater than 180 °, in particular significantly greater 270 °, preferably greater than 300 ° can be achieved. A degree of filling is understood here as meaning the angle which the rolling elements occupy in contact with one another over the circumference.
  • the advantage of a split inner ring over a split outer ring is that less or no lubricant can escape between the inner ring parts which is moved radially outward by centrifugal forces.
  • the input part may have a bearing portion on which a ring of the rolling bearing is arranged.
  • the input part may have a bearing portion on which the inner ring is arranged.
  • the bearing section can be made in one piece with the input part.
  • the bearing portion may be attached to the input part.
  • the bearing portion of the input part may be dome-like.
  • the bearing portion of the input part may be directed toward the output part.
  • the bearing portion of the input part may be a bearing seat.
  • the bearing portion of the input part may have a cylindrical outer surface.
  • the bearing portion of the input part may have an axial abutment shoulder.
  • the inner ring can rest axially against a contact shoulder of the input part.
  • the inner ring can be positively connected to the bearing section.
  • the inner ring can be frictionally connected to the bearing section.
  • the inner ring can be positively and non-positively connected to the bearing section.
  • the output part may have a bearing portion on which the outer ring is arranged.
  • the bearing section can be made in one piece with the output part.
  • the bearing portion may be attached to the output part.
  • the output part may have a hub-like bearing portion.
  • the bearing portion of the output part may be a bearing seat.
  • the bearing portion of the output part may have a cylindrical inner surface.
  • the bearing portion of the output part may have an axial abutment shoulder.
  • the outer ring can rest axially on a contact shoulder of the output part.
  • the abutment shoulder of the output part may be directed against a contact shoulder of the input part.
  • the outer ring of the rolling bearing can be positively connected to the bearing section.
  • the outer ring may be non-positively connected to the bearing section.
  • the outer ring may be positively and non-positively connected to the bearing portion.
  • the rolling elements can be balls.
  • the rolling elements can be cylindrical rollers.
  • Rolling elements can be needles.
  • the rolling elements may be tapered rollers.
  • the rolling elements can be tons.
  • the rolling elements can roll in a groove in the outer ring.
  • the groove in the outer ring can serve as a raceway for the rolling elements.
  • the rolling elements can roll in a groove in the inner ring.
  • the groove in the inner ring can serve as a raceway for the rolling elements.
  • the rolling elements can roll in a groove in the outer ring and in a groove in the inner ring.
  • the rolling bearing can absorb both forces in the radial direction and in the axial direction.
  • the rolling bearing can be designed as a radial bearing.
  • the rolling bearing can be designed as angular contact ball bearings.
  • the rolling bearing may be formed as a single-row angular contact ball bearings.
  • the rolling bearing may be formed such that the rolling elements have four points of contact with the raceways of the rolling bearing.
  • the rolling bearing can be designed as a four-point bearing.
  • Four-point bearings are single-row radial angular contact ball bearings whose raceways are designed so that axial loads can be absorbed in both directions. Radial loads can also be absorbed.
  • the rolling bearing can be designed as a deep groove ball bearing.
  • the rolling bearing can be formed single row.
  • Rolling bodies arranged adjacent to one another in the circumferential direction can be arranged directly next to each other.
  • the rolling bearing can be filled at least approximately fully with rolling elements.
  • the rolling bearing can be filled almost fully with rolling elements.
  • a slight play between the individual adjacent rolling elements avoids contact with each other and an opposite rubbing against each other largely.
  • adjacent arranged rolling elements can be arranged side by side without a cage.
  • fill levels greater than 180 °, in particular greater than 270 °, preferably greater than 300 ° can be achieved. Due to the high degree of filling a uniform distribution of the rolling elements can be achieved in the rolling bearing This can be achieved by the rolling elements without a cage support each other only in the circumferential direction.
  • the inner ring can be divided axially.
  • the inner ring parts can be arranged axially next to each other.
  • the inner ring can be divided in the circumferential direction.
  • the inner ring parts can be arranged side by side in the circumferential direction.
  • a first inner ring part can abut with a contact surface on a contact surface of the second inner ring part, whereby the two contact surfaces approximately form a common contact surface in the assembled state of the rolling bearing.
  • the contact surface can be flat.
  • the contact surface can be curved.
  • the contact surface can be perpendicular to the axis of rotation.
  • the contact surface can run obliquely to the axis of rotation.
  • the contact surface may pass through the groove in the inner ring.
  • the groove may be divided along the contact surface into two groove segments, of which one of the two groove segments is formed in the first inner ring part and the other of the two groove segments is formed in the second inner ring part.
  • the contact surface may extend in the radial direction through the lowest point of the groove of the inner ring.
  • Each of the two groove segments can each have exactly one raceway of a bearing designed as a four-point bearing.
  • the contact surface may extend through the groove of the inner ring such that the inner ring parts have a different width in the axial direction.
  • the rolling bearing can be filled with a lubricant.
  • the rolling bearing can be filled with a grease.
  • the rolling bearing can each have a seal in the axial direction on both sides of the rolling elements. The seals prevent leakage of lubricant in the axial direction of the rolling bearing.
  • the inner ring can be pressed onto a bearing section.
  • the inner ring is frictionally held on the bearing portion in the axial direction.
  • the inner ring can be pressed onto a bearing section with a large overlap.
  • the inner ring parts can be carried at least approximately completely by the bearing section.
  • the inner ring may be positively and / or non-positively connected to the bearing portion, in particular by frictional engagement.
  • the inner ring may abut axially on a step of the bearing section.
  • the step can be an abutment shoulder.
  • the input part may have an abutment shoulder on which the inner ring abuts in the axial direction and in the mounting direction.
  • the input part may have a step on which the inner ring abuts in the axial direction and in the mounting direction.
  • the inner ring can be secured by means of an axial securing of the bearing section in the axial direction against a mounting direction of the inner ring on the bearing section.
  • the formation of the axial securing can be integrated into a final assembly process.
  • the inner ring can be secured by caulking in the axial direction.
  • the inner ring can be secured by means of a flange in the axial direction.
  • the inner ring can be pressed onto a bearing section and additionally secured in the axial direction by means of an axial securing of the bearing section. As a result, very high strengths in the axial direction can be achieved.
  • the inner ring can be pressed onto a bearing section and additionally secured in a form-fitting manner in the axial direction on both sides.
  • the inner ring can abut in the axial direction on the one hand on a step of the bearing section and on the other hand rest against a generated in a final assembly process axial.
  • the inner ring can be pressed onto the bearing section in the axial direction until it bears against the step of the bearing section.
  • the axial securing is formed on the bearing section, so that the step and the axial securing receive the inner ring, consisting of the inner ring parts, between them.
  • the invention thus provides, inter alia, a dual-mass flywheel with a full-spherical four-point bearing.
  • the four-point bearing has a one-piece outer ring, rolling elements, seals on both sides and two inner ring parts.
  • the inner ring parts are pressed with large overlap on the bearing portion and are thus held axially by friction.
  • a variant of the invention provides that the inner rings of the roller bearing are pressed with overlap on the bearing portion and are additionally secured axially via an integrated in the final assembly process caulking / flanging.
  • a possible field of use and purpose of the invention is a rotational and axial guidance of a secondary side relative to a primary side in a dual-mass flywheel for use in drive trains of vehicles with internal combustion engines.
  • the object of the invention is to develop a bearing without a cage with the highest possible number of rolling elements and thereby eliminate a cage.
  • the use of an axially split inner ring makes it possible to equip the entire bearing circumference with balls and thus make the cage superfluous.
  • a torsional vibration damper is provided with a rolling bearing with the highest possible number of rolling elements and the highest possible degree of filling.
  • a torsional vibration damper with an optimized in terms of reliability rolling bearings is provided, with which an input part and an output part of the torsional vibration damper can be mounted rotatably limited relative to each other.
  • the inner ring has at least two structurally separately produced inner ring parts, a degree of filling can be achieved, which makes a cage in the rolling bearing superfluous.
  • bearing failures can be avoided by a cage failure.
  • a torsional vibration damper is provided with a sealed rolling bearing, from which a lubricant can not escape from the interior of the rolling bearing.
  • the lubricant is applied during operation of the rolling bearing by centrifugal forces radially outward. As a result, the lubricant is loaded away from the contact surface between the inner ring parts of the roller bearing, so that leakage of lubricant through the contact surface is avoided.
  • Radially outward the rolling bearing is sealed by an undivided outer ring. In the axial direction, the rolling bearing is sealed on both sides of the rolling elements in each case by a seal.
  • FIG. 1 is a fragmentary view of a dual mass flywheel of a first embodiment
  • Fig. 3 shows the arrangement of the rolling elements in the rolling bearing of Fig. 2 and
  • Fig. 4 is a representation corresponding to Fig. 1 of a second embodiment.
  • Fig. 1 shows schematically and partially a first embodiment of a
  • a dual mass flywheel 100 having an input part 102 and an output part 104.
  • the dual-mass flywheel 100 is used for arrangement in a drive train of a
  • the dual-mass flywheel 100 has an axis of rotation about which the input part 102 and the output part 104 are rotatable together and limited relative to each other rotatable.
  • the axis of rotation defines the direction information used below.
  • a per se known, between the input part 102 and the output part 104 effective spring-damper device is not shown in the figures.
  • the input part 102 has a bearing portion 106.
  • the bearing portion 106 is formed substantially annular and extends in the axial direction.
  • the bearing portion 106 is dome-shaped.
  • the output part 104 has a bearing section 108.
  • the bearing portion 108 is formed substantially annular and extends in the axial direction.
  • the bearing portion 108 is hub-like. Between the bearing portion 106 and the bearing portion 108, a roller bearing 1 10 is arranged.
  • the rolling bearing 1 10 supports the output part 104 on the input part 102 in the radial and axial directions and rotatable relative to each other.
  • the rolling bearing 1 10 shown in FIGS. 1, 2 and 4 has an outer ring 1 12, an inner ring 1 14 and a plurality of arranged in a space between the outer ring 1 12 and the inner ring 1 14 balls 1 16 as rolling elements.
  • the balls 1 16 are respectively on an inner surface of the outer ring 1 12 and on an outer surface of the inner ring 1 14 such that the outer ring 1 12 and the inner ring 1 14 are rotatable relative to each other about the axis of rotation.
  • Between the outer ring 1 12 and the inner ring 1 14 also designed as a sealing discs seals 1 18 are arranged.
  • the balls 1 16 are arranged in the axial direction between the two seals 1 18, without being in contact with them.
  • the seals 1 18 serve to seal the rolling bearing, in particular against the ingress of dirt into the rolling bearing 1 10 and against leakage of lubricant from the rolling bearing 1 10th
  • the rolling bearing 1 10 is a four-point bearing. Each of the balls 1 16 rolls with two points of contact in a groove 120 in the inner surface of the outer ring 1 12 and with two points of contact in a groove 122 in the outer surface of the inner ring 1 14 from. As a result, the balls 1 16 are also guided in the axial direction, so that the outer ring 1 12, the inner ring 1 14 and the balls 1 16 are axially not mutually displaceable.
  • the grooves 120, 122 thus include the running surfaces of the rolling bearing 1 10.
  • the first inner ring part 124 and the second inner ring part 126 each have a contact surface 128 which, in the mounted state of the roller bearing, bear against one another and thereby approximately form a common contact surface 128.
  • the inner ring 1 14 is divided in the circumferential direction along the contact surface 128 which is perpendicular to the axis of rotation of the dual-mass flywheel 100.
  • the inner ring 1 14 consists of two inner ring parts, one
  • the first inner ring part 124 and the second inner ring part 126 are arranged axially next to each other and complement each other to the inner ring 14.
  • the first inner ring part 124 and the second inner ring part 126 abut each other in the contact surface 128.
  • Each of the two inner ring parts 124, 126 has a groove segment 130.
  • the two groove segments 130 together form the groove 122 in the outer surface of the inner ring 14 1.
  • the first inner ring part 124 and the second inner ring part 126 are rotationally symmetrical identical parts and arranged mirror-symmetrically with respect to a plane of symmetry to each other.
  • the plane of symmetry and the contact surface 128 lie on one another.
  • the plane of symmetry passes through the centers of the balls 1 16.
  • the two seals 1 18 are arranged mirror-symmetrically to the plane of symmetry common parts.
  • Fig. 3 shows the arrangement of the balls 1 16 within the rolling bearing 1 10.
  • the balls are distributed in nominal position uniformly over the circumference of the rolling bearing 1 10. Between the surfaces of each two adjacent balls 1 16 there is a distance which is less than the diameter of the balls 1 16.
  • the distance between the surfaces of each two adjacent balls 1 16 is designed so that the balls on the one hand can rotate largely unhindered each other and on the other hand, a large degree of filling is given. In this case, the degree of filling is the angle that the balls 1 16 occupy in contact with each other over the circumference.
  • the first inner ring part 124 and the second inner ring part 126 are each pressed onto the bearing portion 106 of the input part 102.
  • the axial relative position between the inner ring parts 124, 126 and the bearing portion 106 is thus frictionally secured.
  • the first inner ring part 124 bears against a step 132 of the input part 102.
  • the step 132 is formed in a transition region between the bearing portion 106 and a substantially radially extending portion of the input part 102.
  • the step 132 is a contact shoulder on which the inner ring 1 14 axially abuts.
  • the axial relative position between the inner ring parts 124, 126 and the bearing portion 106 is additionally secured in a form-fitting manner by means of the step 132 in an axial direction.
  • the output part 104 has an abutment shoulder 134 on which the outer ring 1 12 abuts axially.
  • the serving as an abutment shoulder 132 of the input part 102 and the abutment shoulder 134 of the outer ring 1 12 are directed counter to each other and support the roller bearing in axially opposite directions.
  • Fig. 4 shows schematically and in part a second embodiment of a
  • Two-mass flywheel 200 with an input part 202 and an output part 204.
  • the second embodiment corresponds to the first embodiment, with the exception of deviating described below features.
  • a roller bearing 1 10 of the dual mass flywheel 200 corresponds in terms of design and operation of the previously described roller bearing 1 10 of the dual mass flywheel 100 and therefore carries the same reference numerals.
  • the first inner ring part 124 and the second inner ring part 126 are each on one
  • Bearing portion 206 of the input part 202 pressed.
  • the axial relative position between the inner ring parts 124, 126 and the bearing portion 206 is thus frictionally secured.
  • the first inner ring part 124 abuts against a step 232 of the input part 202.
  • the step 232 is formed in a transition region between the bearing portion 206 and a substantially radially extending portion of the input part 202.
  • the axial relative position between the inner ring parts 124, 126 and the bearing portion 206 is additionally positively secured by means of the step 232 in a first axial directions.
  • the bearing section 206 has an axial lock 234.
  • the axial securing device 234 engages over the second inner ring part 126 on a face of the second inner ring part 126 facing away from the contact surface 128 in the radial direction. Thereby, the axial relative position between the inner ring parts 124, 126 and the bearing portion 206 against a mounting direction of the inner ring 1 14 secured to the bearing portion 206, in this case opposite to the direction in which the inner ring 1 14 is pressed onto the bearing portion 206.
  • the axial securing device 234 is formed by a forming process that takes place after the first inner ring part 124 and the second inner ring part 126 have been pressed onto the bearing section 206 in a final assembly process.
  • the forming process is caulking and / or beading.
  • the axial securing 234 is designed to be circumferential, but in a modification of the second exemplary embodiment it can also be designed in the form of individual segments. LIST OF REFERENCES

Abstract

L'invention concerne un amortisseur de vibrations de torsion, notamment un volant d'inertie à double masse (100, 200), comprenant une partie d'entrée (102, 202) et une partie de sortie (104, 204, 206) ayant un axe de rotation commun autour duquel la partie d'entrée et la partie de sortie peuvent tourner ensemble et peuvent tourner de manière limitée l'une par rapport à l'autre par l'intermédiaire d'un palier à roulement (110). Le palier à roulement possède une bague extérieure (112), une bague intérieure (114) et plusieurs éléments roulants disposés entre la bague extérieure et la bague intérieure, et la bague intérieure possède au moins deux parties de bague intérieure (124, 126) fabriquées séparément du point de vue structural afin d'améliorer l'amortisseur de vibrations de torsion sur le plan structural et/ou fonctionnel.
EP15725491.3A 2014-05-20 2015-04-28 Amortisseur de vibrations de torsion Withdrawn EP3146233A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014209486 2014-05-20
PCT/DE2015/200282 WO2015176722A1 (fr) 2014-05-20 2015-04-28 Amortisseur de vibrations de torsion

Publications (1)

Publication Number Publication Date
EP3146233A1 true EP3146233A1 (fr) 2017-03-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP15725491.3A Withdrawn EP3146233A1 (fr) 2014-05-20 2015-04-28 Amortisseur de vibrations de torsion

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EP (1) EP3146233A1 (fr)
CN (1) CN106461006A (fr)
DE (1) DE112015002370A5 (fr)
WO (1) WO2015176722A1 (fr)

Families Citing this family (4)

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Publication number Priority date Publication date Assignee Title
DE102016203956A1 (de) 2016-03-10 2017-09-14 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer
EP3891416A1 (fr) * 2018-10-23 2021-10-13 Schaeffler Technologies AG & Co. KG Amortisseur de vibrations de torsion
DE102019118971A1 (de) * 2019-07-12 2021-01-14 Schaeffler Technologies AG & Co. KG Torsionsschwingungsdämpfer
DE102019120004A1 (de) * 2019-07-24 2021-01-28 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer

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US3980359A (en) * 1975-05-08 1976-09-14 United Technologies Corporation Ball bearing
GB2269864A (en) * 1992-08-20 1994-02-23 Fichtel & Sachs Ag A sealed bearing assembly.
US5768950A (en) * 1995-07-01 1998-06-23 Fichtel & Sachs Ag Flywheel device having a sealing for a grease chamber
DE19809176A1 (de) * 1998-03-04 1999-09-09 Schaeffler Waelzlager Ohg Schwungrad

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CN106461006A (zh) 2017-02-22
WO2015176722A1 (fr) 2015-11-26

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