CN106461006A - Torsional vibration damper - Google Patents
Torsional vibration damper Download PDFInfo
- Publication number
- CN106461006A CN106461006A CN201580025507.5A CN201580025507A CN106461006A CN 106461006 A CN106461006 A CN 106461006A CN 201580025507 A CN201580025507 A CN 201580025507A CN 106461006 A CN106461006 A CN 106461006A
- Authority
- CN
- China
- Prior art keywords
- internal ring
- bearing
- vibration damper
- torsional vibration
- 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.)
- Pending
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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
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- 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
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- 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
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- 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
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
The invention relates to a torsional vibration damper, in particular a two-mass flywheel (100, 200), comprising an input part (102, 202) and an output part (104, 204, 206) with a common axis of rotation, around which the input part and the output part are rotatable together and are rotatable to a limited extent relative to each other by means of a rolling bearing (110), wherein the rolling bearing has an outer ring (112), an inner ring (114) and a plurality of rolling bodies arranged between the outer ring and the inner ring. The inner ring comprises at least two inner ring parts (124, 126) which are produced in a structurally separate manner in order to structurally and/or functionally improve the torsional vibration damper.
Description
Technical field
The present invention relates to a kind of torsional vibration damper, especially a kind of double mass flywheel, with common axis of rotation line
Input component and output, input component and output can rotate around the common axis of rotation line together and can be by means of rolling
Bearing is relative to each other limitedly reversed, and wherein, rolling bearing has outer shroud, internal ring and multiple is arranged between outer shroud and internal ring
Rolling element.
Background technology
From the German patent application with document number DE 10 2,013 204 233.7 that submits on March 12nd, 2013
Know a kind of double mass flywheel, with two rotating masses that can limitedly reverse around rotation axiss and arrangement between them,
The rolling bearing of the rotational supporting structure of the axial restraint of the rotating mass is provided, the rolling bearing has inner ring and outer rings
With the rolling element rolled on their guide rail, in the double mass flywheel, the compactedness of rolling element is more than or equal to 180 ° simultaneously
And rolling physical ability is shifted in circumferential direction relative to each other.Here, compactedness is interpreted as an angle, rolling element is contiguously mutual
Occupy the angle when reclining in the circumferential.In order to reach the compactedness more than or equal to 180 °, the outer shroud split of rolling bearing
Formula ground construction.Thus, it is possible to assemble be especially configured to 4 points of bearings or groove ball bearing, have than from prior art
The rolling bearing of possible higher compactedness in the case of the rolling bearing of the outer shroud with one that knows.
Generally from the assembly method for rolling bearing known in the art, the rolling bearing has the interior of not split
Ring, the outer shroud of not split and the rolling element rolled in the groove of inner ring and outer rings.Here is arranged, in the first installation step, rolling
Kinetoplast mutually snugly loads in outer shroud.Then, internal ring loads in outer shroud in the position of centrifugation.Now, it follows that rolling
The quantity of the maximum of the rolling element of dynamic bearing：Only when rolling element mutually recline in circumferential limited subregion without
When rolling element is arranged in opposite region, internal ring eccentrically can load so that internal ring can be to described without rolling element
Region direction eccentrically shift.In another installation step, internal ring is brought in concentric position relative to outer shroud.Then
Rolling element is distributed at circumferential upper and is fixed with cage.However, can only be realized less than 180 ° by this assembly method
Compactedness.
Content of the invention
The present invention is based on following tasks：Torsional vibration damper introductory song described in is improved in structure and/or functionally.Especially to
The torsional vibration damper with rolling bearing is provided, the rolling bearing has the rolling element of high quantity as far as possible.To especially provide
There is the torsional vibration damper of rolling bearing, the rolling bearing there is compactedness as high as possible.To especially provide and have in event
The torsional vibration damper of the rolling bearing optimized in terms of barrier safety, the input component and output of torsional vibration damper can pass through described
Rolling bearing is supported by the way of it limitedly can reverse relative to each other.Torsional oscillation vibration damping with rolling bearing will be especially provided
Device, the rolling bearing are avoided due to the bearing fault of cage failure.Torsional vibration damper with rolling bearing will be especially provided,
The rolling bearing is constructed in the way of without cage.Torsional vibration damper with sealed rolling bearing will be especially provided, by
Can not overflow from the inside of rolling bearing in the sealed rolling bearing lubrication agent.
By torsional vibration damper, especially double mass flywheel, the solution of the task realizes that the torsional vibration damper has band
There are the input component and output of common axis of rotation line, the input component and the output can be around the common axis of rotation line together
Rotate and can be limitedly reversed by means of rolling bearing relative to each other, wherein, rolling bearing has outer shroud, internal ring and multiple
The rolling element being arranged between outer shroud and internal ring, in the rolling bearing, the internal ring has at least two to divide in structure
The internal ring part of body formula ground manufacture.
Torsional vibration damper can be double mass flywheel.Disclose for double mass flywheel in 42 39 770 C2 of DE
Example.Torsional vibration damper can be that the auxiliary unit of the starter for being for example used for internal combustion engine drives vibroshock.Torsional vibration damper can
Being clutch damper.Torsional vibration damper can be used in being arranged in the drivetrain of motor vehicles.Drivetrain can have internal combustion
Machine.Drivetrain can have friction clutch device.Drivetrain can have variator.Drivetrain can have at least one energy
The wheel of driving.Torsional vibration damper can be used in being arranged between internal combustion engine and friction clutch device.Torsional vibration damper can
For reducing torsional oscillation, the torsional oscillation is especially in internal combustion engine as periodic process is excited.Input component can be used in especially
It is connected in driving side with internal combustion engine.Output can be used in especially being connected in slave end with friction clutch device.Term " input
Part " and " output " are related to the power flow direction for especially sending from internal combustion engine.
Drivetrain could be for the hybrid drive train of motor vehicles.The drivetrain can be combination drive in parallel
System.Drivetrain can be full hybrid drive train.Drivetrain can have the first energy transducer and the second energy transducer.
First energy transducer can be used in for chemical energy being converted to kinetic energy.Internal combustion engine can be the first energy transducer.Internal combustion function
Enough by means of such as gasoline, diesel oil, liquefied gas (Liquefied Petroleum Gas, LPG, GPL), compressed natural gas
(Compressed Natural Gas, CNG) or carbon as liquefied natural gas (Liquefied Natural Gas, LNG)
Hydrogen compound runs.Internal combustion engine can be run by means of hydrogen.In order to give the first energy transducer energy supply, the first storage can be set
Can device.First accumulator can be fluid tank.Second energy transducer can be used in converting electrical energy into kinetic energy.Motor can
Being the second energy transducer.Motor can be used as motor running.Motor can be used as generator operation.Motor can be in knot
Merge motor and electromotor on structure.In order to give the second energy transducer energy supply, the second accumulator can be set.Second accumulator
It can be electric energy accumulator.Second energy transducer can be accumulator.First energy transducer and/or the second energy transducer energy
It is enough in alternatively or is driven in parallel motor vehicles.
Spring cushion device can work between input component and output.When torsional vibration damper runs, input
Part and output can resist the power of spring cushion device and reverse relative to each other.Spring cushion device can have friction dress
Put.Spring cushion device can have spring assembly.Spring assembly can have at least one accumulator.Described at least one
Accumulator can have at least one spring.At least one spring can be compression spring.At least one spring can
Being helical spring.At least one spring can be arc spring.At least one accumulator can have the first bullet
Spring and second spring.First spring and second spring mutually can be arranged on sleeve connection ground.At least one accumulator can
Work in glide direction and/or in lead.Glide direction is directed towards the power flow direction of internal combustion engine sensing.Traction side
To being the power flow direction that sends from internal combustion engine.
During the assembling process of the rolling bearing of the torsional vibration damper according to the present invention, rolling element can be positioned at first
The internal ring inside outer shroud and being then made up of in structure split type the internal ring part for manufacturing is assembled.Due to using split
The internal ring of formula, in last installation step a step, can be in the case where the ball of high quantity be received described in assembling
Internal ring part.Thus, it is possible to realizing significantly greater than 180 °, being especially apparent more than 270 °, preferably greater than 300 ° of compactedness.Here,
Compactedness is interpreted as that an angle, rolling element take the angle in the circumferential when contiguously mutually reclining.Split type internal ring phase
Advantage for split type outer shroud is, can overflow less lubricant or do not spill over lubrication between internal ring part
Agent, the lubricant are moved to radially outer due to centrifugal force.
Input component can have bearing segment, arrange the ring of rolling bearing on the bearing segment.Input component can have
Bearing segment, arranges internal ring on the bearing segment.Bearing segment can integratedly be implemented with input component.Bearing segment can be consolidated
It is scheduled on input component.The bearing segment of input component can be raised water (domartig).The bearing segment of input component being capable of court
Orient to output.The bearing segment of input component can be bearing block.The bearing segment of input component can have the appearance of cylindricality
Face.The bearing segment of input component can have the bearing shoulder of axial direction.Internal ring can abut in the supporting of input component in the axial direction
On shoulder.Internal ring can with bearing segment shape sealed be connected.Internal ring can with bearing segment force closure be connected.Internal ring can
With with bearing segment shape sealed and force closure be connected.
Output can have bearing segment, arrange outer shroud on the bearing segment.Bearing segment can be with output one
Implement on body ground.Bearing segment can be fixed on output.Thus provide simple and prove effective bearing arrangement.Output can
With the bearing segment with hub.The bearing segment of output can be bearing block.The bearing segment of output can have post
The inner surface of shape.The bearing segment of output can have the bearing shoulder of axial direction.Outer shroud can abut in output in the axial direction
On the bearing shoulder of part.The bearing shoulder of output can be oriented against the bearing shoulder of input component.The outer shroud of rolling bearing can
With with bearing segment shape sealed be connected.The outer shroud can with bearing segment force closure be connected.The outer shroud can be with bearing
Segment shape is sealed and force closure ground connects.
Rolling element can be ball.Rolling element can be cylinder roller.Rolling element can be needle roller.Rolling element can be taper
Roller.Rolling element can be bucket.Roll in the groove that rolling element can be in outer shroud.Groove in outer shroud can act as rolling
The guide rail of body.Roll in the groove that rolling element can be in internal ring.Groove in internal ring can act as the guide rail of rolling element.Rolling
Kinetoplast can be in outer shroud groove in and internal ring in groove in roll.Thus, rolling bearing is not only able to receive radially
Power on direction and power in the axial direction can be received.Rolling bearing is so structured that journal bearing.Rolling bearing can
To be configured to angular contact ball bearing.Rolling bearing is so structured that single-row angular contact ball bearing.Rolling element can be constructed as below：Make
Obtain the contact point that rolling element has four and the guide rail contact of rolling bearing.Rolling bearing is so structured that 4 points of bearings.4 points
Bearing is single-row radial direction angular contact ball bearing, and the guide rail of the single-row radial direction angular contact ball bearing is constructed as below：So that axially negative
Lotus can be received in the two directions.Radial load can equally be received.Rolling bearing is so structured that groove ball bearing.
Rolling bearing can be constructed with single-row.
The rolling element that arranges adjacent to each other in circumferential direction directly can be arranged side by side.Rolling bearing can be at least
Almost filled with rolling element completely.Rolling bearing almost can be filled with rolling element completely.Adjacent single rolling element it
Between small gap be avoided as much as mutual contact and mutually to friction.It is adjacent in circumferential direction each other
The rolling element of arrangement can be arranged side by side in the case of without cage.Thus, it is possible to realize more than 180 °, especially greater than 270 °,
Preferably greater than 300 ° of compactedness.Can realize that rolling element is uniformly distributed in rolling bearing by high compactedness.This energy
Enough it is accomplished by：In the case of without cage, rolling element is only mutually supported in circumferential direction.In adjacent list
Small gap can be set between individual rolling element.The cage diminished relative to prior art can be arranged between rolling element.
Internal ring can separate in the axial direction.Internal ring part can be arranged side by side in the axial direction.Internal ring can be in circumferential side
Separate upwards.Internal ring part can be arranged side by side in circumferential direction.
On the contact surface of the second internal ring part, thus first internal ring part can be abutted in contact surface, two contact surfaces
Common contact surface is nearly formed in the state of rolling bearing is assembled.The contact surface can be flat.The contact surface can be with
It is bending.The contact surface can extend perpendicular to rotation axiss.The contact surface can obliquely extend relative to rotation axiss.
The contact surface can be passed through the groove in internal ring and extend.The groove can be divided into two groove segments along contact surface, this two
In individual groove segment, a groove segment in described two groove segments is constructed in the first internal ring part, and described two grooves
Another groove segment in section is constructed in the second internal ring part.Thus, internal ring part is made to be embodied as same pieces, this especially saves
Instrument cost.The contact surface can in radial directions through the minimum point extension of the groove of internal ring.Described two grooves
Each in section can be respectively provided with what a guide rail proper of the rolling bearing for being embodied as 4 points of bearings.The contact surface can be as
This extends through the groove of internal ring：So that internal ring part has different width in the axial direction.
Rolling bearing with lubricator can be filled.Rolling bearing can use fat filling.Rolling bearing can be in axial side
Sealing member is respectively provided with upwards in rolling element both sides.The sealing member prevents lubricant from overflowing from rolling bearing in the axial direction
Go out.
Internal ring can be pressed on bearing segment.Therefore, frictional force is maintained at axle to internal ring in locking manner in the axial direction
Hold on section.Internal ring can be pressed on bearing segment with big coverage.Internal ring part can at least almost completely by axle
Hold section carrying.Internal ring can be connected cohesively together with bearing segment shape sealed and/or force closure, especially frictional force.Internal ring can
Abutted on the end difference of bearing segment in the axial direction.The end difference can be bearing shoulder.Input component can have
Shoulder is held, internal ring is abutted on the bearing shoulder in the axial direction and on assembly direction.Input component can have ladder
Portion, internal ring are abutted on the end difference in the axial direction and on assembly direction.
Internal ring can be in reverse to internal ring in bearing segment in the axial direction by means of the axial relief device of bearing segment
On assembly direction fix.Here, the construction of axial relief device is desirably integrated in final assembling process.Internal ring can be by
Fixed in compacting (Verstemmung) in the axial direction.Internal ring can be fixed in the axial direction by means of crimping.Internal ring can
To be forced on bearing segment and additionally the axial relief device by means of bearing segment is fixed in the axial direction.By
This achieves intensity very high in the axial direction.Internal ring can be forced on bearing segment and in the axial direction
Additionally both sides shape sealed fixed.On the one hand internal ring can be abutted on the end difference of bearing segment in the axial direction
And on the other hand abut on the axial relief device produced in final assembling process.Here, in period of assembly, internal ring exists
It is pressed on axial direction on bearing segment until following degree：The internal ring is abutted on the end difference of bearing segment.Then,
Axial safety are constructed on bearing segment so that the internal ring being made up of internal ring part is connect by end difference and axial relief device
It is received between the end difference and axial relief device.
Therefore, briefly and in other words, by present invention particularly provides with the double quality without 4 points of ball bearings of retainer
Flywheel.4 points of bearings have outer shroud, rolling element, the sealing member of both sides and two internal ring parts of one.The internal ring part
It is pressed on bearing segment with big coverage and is therefore axially kept by friction.A kind of modification of the present invention sets
Put, the internal ring of rolling bearing is pressed on bearing segment with coverage and additionally by being integrated in final assembling process
Compacting/crimping fix in the axial direction.The present invention feasible use range and application target be：There is internal combustion engine being used in
In double mass flywheel in the power train of vehicle, primary side is guided pivotably and in the axial direction relative to primary side.Logical
Cross the present invention and especially solve following tasks：Exploitation has the bearing of the rolling element of quantity as much as possible in the case of without cage
Structure and thus removing cage.Internal ring split type in the axial direction using realize overall bearing circumferentially equipped with ball and
Hence in so that cage becomes unnecessary.Relative to from known to industrial circle, blow-by and 4 points of axles being connected in fuel feeding portion
Hold, the present invention has the sealable rolling bearing for sealing in other words.Additionally, in the double mass flywheel with rolling bearing,
Shortcoming described below is avoided by the ring for closing：The cage for making ball be evenly distributed in whole bearing circumference operationally meets with
Stress and abrasion.Thus the destruction of cage may occur, or thus cage may lose its function：The cage is moved in the axial direction.
In the case of the guiding without cage, ball is likely to accumulate on a bearing side.Thus, bearing loses the function being coaxially oriented to
And damage double mass flywheel.
The optional feature of the present invention is especially described with " can with ".Therefore, following enforcements of the present invention are respectively present
Example：The embodiment has a respective feature or some features.
The torsional vibration damper with rolling bearing is provided by the present invention, and the rolling bearing is with high quantity as far as possible
Rolling element and compactedness as high as possible.The torsional vibration damper with the rolling bearing optimized in terms of fail safe is provided,
The side of the input component and output of torsional vibration damper limitedly reversing relative to each other can be made by means of the rolling bearing
Formula is supported by.Internal ring has at least two internal ring parts for manufacturing in structure split typely, thus, it is possible to realize following fillings
Degree：The compactedness causes cage to become unnecessary in rolling bearing.Therefore, it is possible to avoid due to the bearing fault of outer housing failure.
Further it is provided that a kind of torsional vibration damper of the Packed rolling bearing of tool, due to the rolling bearing of the sealing, lubricant can not be from
Overflow the inside of rolling bearing.In rolling bearing run duration, apply lubricant from centrifugal force to radially outer.Thus lubrication is made
Agent is loaded away from the contact surface between the internal ring part of rolling bearing, so as to avoid lubricant from overflowing by contact surface.Rolling
Dynamic bearing is by not split type outer shroud diametrically to external seal.In the axial direction, rolling bearing is in rolling element both sides point
Do not sealed by sealing member.
Description of the drawings
Two embodiments of the present invention are explained with reference to the accompanying drawings.Other feature and excellent is drawn from the explanation
Point.
Schematically and it is exemplarily illustrated：
The part diagram of the double mass flywheel of Fig. 1 first embodiments,
Half sections of the Fig. 2 through the rolling bearing of the double mass flywheel according to the present invention；
The arrangement of rolling elements of the Fig. 3 in the rolling bearing of Fig. 2, and
The diagram corresponding to Fig. 1 of Fig. 4 second embodiments.
Specific embodiment
Fig. 1 schematically and partly illustrates first of the double mass flywheel 100 with input component 102 and output 104
Embodiment.
Double mass flywheel 100 is used for being arranged in the drivetrain of motor vehicles, is especially arranged in internal combustion engine and friction clutch
Between.Double mass flywheel 100 has rotation axiss, and input component 102 and output 104 can be around the rotation axiss common rotations simultaneously
And limitedly can reverse relative to each other.Rotation axiss definition underneath with direction indicate.Not shown in the accompanying drawings known,
The spring cushion device worked between input component 102 and output 104.
Input component 102 has bearing segment 106.Bearing segment 106 as far as possible annularly construction and in the axial direction
Extend.Bearing segment 106 is raised water.Output 104 has bearing segment 108.The annularly structure as far as possible of bearing segment 108
Make and extend in the axial direction.Bearing segment 108 is hub.Arrange between bearing segment 106 and bearing segment 108
There is rolling bearing 110.Rolling bearing 110 makes output 104 be bearing on input component 102 in the radial and axial directions and energy
Reverse relative to each other.
Rolling bearing 110 shown in Fig. 1,2 and 4 has outer shroud 112, internal ring 114 and multiple in 112 and of outer shroud
The ball 116 that arranges as rolling element in installing space between internal ring 114.The ball 116 so abuts in outer shroud 112 respectively
On inner surface and on the outer surface of internal ring 114：Outer shroud 112 and internal ring 114 are rotated around rotation axiss relative to each other.This
Outward, two sealing members 118 for being embodied as seal disc are disposed between outer shroud 112 and internal ring 114.Ball 116 is in the axial direction
It is arranged between two sealing members 118, and does not contact with the sealing member.Sealing member 118 is used for sealed rolling bearing, especially prevents
Only pollutant are entered in rolling bearing 110 and prevent lubricant from overflowing from rolling bearing 110.
Rolling bearing 110 is 4 points of bearings.Each in ball 116 is with two contact points in the inner surface of outer shroud 112
Roll in groove 120 and with rolling in groove 122 of two contact points in the outer surface of internal ring 114.Thus ball 116 also can
Enough it is directed in axial direction so that outer shroud 112, internal ring 114 and ball 116 cannot move relative to each other in the axial direction.Therefore,
Groove 120,122 includes the guide rail of rolling bearing 110.
First internal ring part 124 and the second internal ring part 126 are respectively provided with contact surface 128, and the contact surface is in the axis of rolling
Take up and in the state of preparing, mutually recline and thus nearly form common contact surface 128.The edge in circumferential direction of internal ring 114
Contact surface 128 to separate, the contact surface extends perpendicular to the rotation axiss of double mass flywheel 100.Therefore, internal ring 114 is by two
Individual internal ring part, i.e. the first internal ring part 124 and the second internal ring part 126 are constituted.First internal ring part 124 and the second internal ring portion
Part 126 is arranged side by side in the axial direction and complementation is into the internal ring 114.First internal ring part 124 and the second internal ring part 126
Mutually recline in contact surface 128.Each in two internal ring parts 124,126 has groove segment 130.Two groove segments 130
The groove 122 being formed in the outer surface of internal ring 114 together.
First internal ring part 124 and the second internal ring part 126 are the same pieces that symmetrically construct and with regard to symmetrical
Arrange mirror one anotherly in face.The plane of symmetry and contact surface 128 overlap each other.The plane of symmetry extends through the midpoint of ball 116.Two
Sealing member 118 is the same pieces relative to plane of symmetry specular.
Fig. 3 illustrates arrangement of the ball 116 inside rolling bearing 110.Ball is evenly distributed in the axis of rolling in nominal position
Hold in 110 circumference.The spacing of the diameter less than ball 116 is there is between the surface of the adjacent ball 116 of each two.Per two
Spacing between the surface of individual adjacent ball 116 is designed as follows：So that the ball on the one hand as far as possible being capable of phase in the clear
Mutually rotate and on the other hand there is big compactedness.Here, compactedness be ball 116 when contiguously mutually reclining in circumference
On the angle that occupies.
First internal ring part 124 and the second internal ring part 126 are forced on the bearing segment 106 of input component 102 respectively.
Therefore, the relative position frictional force in the axial direction between internal ring part 124,126 and bearing segment 106 is fixed in locking manner.The
One internal ring part 124 is abutted on the end difference 132 of input component 102.End difference 132 is constructed in bearing segment 106 and input component
In transitional region between 102 region for extending in radial directions to a great extent.End difference 132 is bearing shoulder,
Internal ring 114 is abutted on the bearing shoulder in the axial direction.Axial direction between internal ring part 124,126 and bearing segment 106
Relative position by means of end difference 132 in the axial direction additionally shape sealed fixed.
There is output 104 bearing shoulder 134, outer shroud 112 are abutted on the bearing shoulder in the axial direction.Input component
102 end difference 132 as bearing shoulder and the bearing shoulder 134 of outer shroud 112 are oriented reversely with each otherly, and in the axial direction
Rolling bearing is supported on the direction for oppositely orienting.
Fig. 4 schematically and partly illustrates second of the double mass flywheel 200 with input component 202 and output 204
Embodiment.In terms of structurally and functionally principle, in addition to the following feature for differently illustrating, second embodiment corresponds to first
Embodiment.
In terms of structurally and functionally principle, the rolling bearing 110 of double mass flywheel 200 corresponds to double matter illustrated before
The rolling bearing 110 of amount flywheel 100, and therefore have identical reference.
First internal ring part 124 and the second internal ring part 126 are forced on the bearing segment 206 of input component 202 respectively.
Therefore, the relative position frictional force in the axial direction between internal ring part 124,126 and bearing segment 206 is fixed in locking manner.The
One internal ring part 124 is abutted on the end difference 232 of input component 202.End difference 232 is constructed in bearing segment 206 and input component
In 202 transitional region as far as possible between the upwardly extending region in side of radial direction.In internal ring part 124,126 and bearing area
Section 206 between axial direction on relative position by means of end difference 232 on the first axial direction additionally shape sealed solid
Fixed.
In bearing segment 206 on the end of end difference 232, bearing segment 206 has axial relief device 234.
Axial relief device 234 is overlapped in second on the end face of contact surface 128 in the second internal ring part 126 in radial directions
Ring component 126.Thus, the relative position in the axial direction between internal ring part 124,126 and bearing segment 206 is in reverse to internal ring
114 assembly directions on bearing segment 206 are fixed, and are in reverse to following directions at present and are fixed：Internal ring 114 in this direction by
It is pressed on bearing segment 206.Axial relief device 234 is consisted of forming process, by the first internal ring part 124 and second
After internal ring part 126 is pressed on bearing segment 206, the forming process is carried out in final assembling process.The molding
Journey is compacting and/or crimping.Axial relief device 234 is circumferentially constructed, but also can be with the modification of second embodiment
The form of single section is constructing.
Reference numerals list
100 double mass flywheels
102 input components
104 outputs
106 bearing segments
108 bearing segments
110 rolling bearings
112 outer shrouds
114 internal ring
116 balls, rolling element
118 sealing members
120 grooves
122 grooves
124 first internal ring parts
126 second internal ring parts
128 contact surfaces
130 groove segments
132 end differences, bearing shoulder
134 bearing shoulders
200 double mass flywheels
202 input components
204 outputs
206 bearing segments
232 end differences
234 axial relief devices
Claims (10)
1. torsional vibration damper, especially double mass flywheel (100,200), with common axis of rotation line input component (102,
202) and output (104,204), input component (102,202) and the output (104,204) can around described jointly
Rotation axiss are rotated together and can be limitedly reversed by means of rolling bearing (110) relative to each other, wherein, the axis of rolling
(110) are held with outer shroud (112), internal ring (114) and multiple is arranged between the outer shroud (112) and the internal ring (114)
Rolling element (116), it is characterised in that described internal ring (114) have at least two internal ring portions for manufacturing in structure split typely
Part (124,126).
2. torsional vibration damper according to claim 1, it is characterised in that described input component (102,202) have bearing area
Section (106,206), internal ring (114) are arranged on the bearing segment, and the output (104,204) has bearing area
Section (108,208), outer shroud (112) are arranged on the bearing segment.
3. the torsional vibration damper according at least one in the claims, it is characterised in that rolling bearing (110)
For single-row angular contact ball bearing, especially 4 points bearings.
4. the torsional vibration damper according at least one in the claims, it is characterised in that rolling bearing (110)
At least almost filled with rolling element completely.
5. the torsional vibration damper according at least one in the claims, it is characterised in that the internal ring part (124,
126) contact surface (128) for being arranged side by side in the axial direction and facing each other mutually reclines.
6. the torsional vibration damper according at least one in the claims, it is characterised in that the internal ring part (124,
126) at least almost carried by the bearing segment (106,206) completely.
7. the torsional vibration damper according to any one of claim 3 to 6, it is characterised in that described internal ring (114) have and use
In the groove (122) of the rolling element (116), and the groove (122) is divided into two grooves along the contact surface (128)
Section (130), in the two groove segments, a groove segment in described two groove segment (130) is constructed in first internal ring
In part (124), also, another groove segment in described two groove segments (130) is constructed in the second internal ring part
(126) in.
8. the torsional vibration damper according at least one in the claims, it is characterised in that rolling bearing (110)
Sealing member (118) is respectively provided with the rolling element (116) both sides.
9. the torsional vibration damper according at least one in claim 2 to 8, it is characterised in that internal ring (114) are pressed
It is tightened on the bearing segment (106,206).
10. the torsional vibration damper according at least one in claim 2 to 9, it is characterised in that internal ring (114) borrow
The axial relief device (234) for helping the bearing segment (206) is in reverse to the internal ring (114) in the axial direction described
Assembly direction on bearing segment (206) is fixed.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102014209486 | 2014-05-20 | ||
| DE102014209486.0 | 2014-05-20 | ||
| PCT/DE2015/200282 WO2015176722A1 (en) | 2014-05-20 | 2015-04-28 | Torsional vibration damper |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106461006A true CN106461006A (en) | 2017-02-22 |
Family
ID=53274328
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580025507.5A Pending CN106461006A (en) | 2014-05-20 | 2015-04-28 | Torsional vibration damper |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP3146233A1 (en) |
| CN (1) | CN106461006A (en) |
| DE (1) | DE112015002370A5 (en) |
| WO (1) | WO2015176722A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112283296A (en) * | 2019-07-24 | 2021-01-29 | 舍弗勒技术股份两合公司 | Torsional vibration damper |
| CN113825926A (en) * | 2019-07-12 | 2021-12-21 | 舍弗勒技术股份两合公司 | Torsional vibration damper |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102016203956A1 (en) | 2016-03-10 | 2017-09-14 | Schaeffler Technologies AG & Co. KG | torsional vibration dampers |
| EP3891416A1 (en) * | 2018-10-23 | 2021-10-13 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper |
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|---|---|---|---|---|
| GB2184518A (en) * | 1985-12-19 | 1987-06-24 | Luk Lamellen & Kupplungsbau | Arrangement for compensating for rotary shocks |
| EP0239457A1 (en) * | 1986-03-14 | 1987-09-30 | Valeo | Transmission-damping disc, in particular for a motor car |
| FR2617934A1 (en) * | 1987-04-08 | 1989-01-13 | Valeo | Damping flywheel for a torque-transmission device, incorporating a rolling-contact bearing with two rows of rolling elements |
| DE8420404U1 (en) * | 1984-07-07 | 1992-12-10 | Luk Lamellen Und Kupplungsbau Gmbh, 7580 Buehl, De | |
| CN1120637A (en) * | 1994-07-20 | 1996-04-17 | 菲希特尔及萨克斯有限公司 | Double plate fly wheel cooled with air |
| CN1221080A (en) * | 1994-07-15 | 1999-06-30 | 曼内斯曼·萨克斯股份公司 | Divided flywheel apparatus |
| CN1296555A (en) * | 1998-04-06 | 2001-05-23 | 卢克摩擦片和离合器有限公司 | Divided flywheel |
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|---|---|---|---|---|
| US3980359A (en) * | 1975-05-08 | 1976-09-14 | United Technologies Corporation | Ball bearing |
| DE4239770C2 (en) | 1991-12-05 | 2003-06-18 | Luk Lamellen & Kupplungsbau | Dual Mass Flywheel |
| US5533815A (en) * | 1992-08-20 | 1996-07-09 | Fichtel & Sachs Ag | Bearing arrangement for a device comprising two rotating components |
| DE19524100C1 (en) * | 1995-07-01 | 1996-07-11 | Fichtel & Sachs Ag | Flywheel arrangement, esp. for vehicle clutch |
| DE19809176A1 (en) * | 1998-03-04 | 1999-09-09 | Schaeffler Waelzlager Ohg | flywheel |
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2015
- 2015-04-28 DE DE112015002370.4T patent/DE112015002370A5/en not_active Withdrawn
- 2015-04-28 CN CN201580025507.5A patent/CN106461006A/en active Pending
- 2015-04-28 WO PCT/DE2015/200282 patent/WO2015176722A1/en active Application Filing
- 2015-04-28 EP EP15725491.3A patent/EP3146233A1/en not_active Withdrawn
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|---|---|---|---|---|
| DE8420404U1 (en) * | 1984-07-07 | 1992-12-10 | Luk Lamellen Und Kupplungsbau Gmbh, 7580 Buehl, De | |
| GB2184518A (en) * | 1985-12-19 | 1987-06-24 | Luk Lamellen & Kupplungsbau | Arrangement for compensating for rotary shocks |
| EP0239457A1 (en) * | 1986-03-14 | 1987-09-30 | Valeo | Transmission-damping disc, in particular for a motor car |
| FR2617934A1 (en) * | 1987-04-08 | 1989-01-13 | Valeo | Damping flywheel for a torque-transmission device, incorporating a rolling-contact bearing with two rows of rolling elements |
| CN1221080A (en) * | 1994-07-15 | 1999-06-30 | 曼内斯曼·萨克斯股份公司 | Divided flywheel apparatus |
| CN1120637A (en) * | 1994-07-20 | 1996-04-17 | 菲希特尔及萨克斯有限公司 | Double plate fly wheel cooled with air |
| CN1296555A (en) * | 1998-04-06 | 2001-05-23 | 卢克摩擦片和离合器有限公司 | Divided flywheel |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113825926A (en) * | 2019-07-12 | 2021-12-21 | 舍弗勒技术股份两合公司 | Torsional vibration damper |
| CN112283296A (en) * | 2019-07-24 | 2021-01-29 | 舍弗勒技术股份两合公司 | Torsional vibration damper |
| CN112283296B (en) * | 2019-07-24 | 2024-04-12 | 舍弗勒技术股份两合公司 | Torsional vibration damper |
Also Published As
| Publication number | Publication date |
|---|---|
| EP3146233A1 (en) | 2017-03-29 |
| WO2015176722A1 (en) | 2015-11-26 |
| DE112015002370A5 (en) | 2017-02-16 |
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Application publication date: 20170222 |
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