CN107701656A - Torsional vibration damper - Google Patents
Torsional vibration damper Download PDFInfo
- Publication number
- CN107701656A CN107701656A CN201710584860.8A CN201710584860A CN107701656A CN 107701656 A CN107701656 A CN 107701656A CN 201710584860 A CN201710584860 A CN 201710584860A CN 107701656 A CN107701656 A CN 107701656A
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- China
- Prior art keywords
- support section
- section
- output
- torsional vibration
- vibration damper
- 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.)
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Classifications
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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
- 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
- F16F15/30—Flywheels
- F16F15/315—Flywheels characterised by their supporting arrangement, e.g. mountings, cages, securing inertia member to shaft
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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
- 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
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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
- 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
- F16F15/30—Flywheels
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Torsional vibration damper (100), especially double mass flywheel, the torsional vibration damper (100) have：Input component (102) with cover region section (110) and the output (104) with common rotation axis (106), the input component (102) and the output (104) can together be rotated around the pivot center and limitedly reversed relative to each other；The supporting arrangement (107) being arranged between the input component (102) and the output (104) and the spring damper to be worked between the input component (102) and output (104),The supporting arrangement (107) can angular movement wherein,And the input component (102) has at least one first support section being used to be supported on the output (104),And the output (104) has at least one second support section being used to be supported on the input component (102),Wherein,The support section is mutually corresponding,The support section diametrically separates spacing with the supporting arrangement (107),And worked from the pre-determined tilt angle between the input component (102) and the output (104),In structure and/or functionally to improve the torsional vibration damper (100).
Description
Technical field
The present invention relates to a kind of torsional vibration damper, especially double mass flywheel, the torsional vibration damper has：Turn with common
The input component and output of shaft line, the input component and the output can together rotate around the pivot center and being capable of phases
To limitedly reversing each other；The supporting arrangement being arranged between the input component and the output；With in the input component and output
Between the spring damper that works, the spring damper has spring assembly and rubbing device.
Background technology
A kind of torsional vibration damper, especially double mass flywheel as known to the A1 of patent document DE 10 2,013 210 492, should
Torsional vibration damper has：Input component and output with common rotation axis, the input component and the output can surround should
Pivot center common rotation and can limitedly it reverse relative to each other；The bullet to be worked between the input component and the output
Spring vibration absorber；With the supporting arrangement mutually supported for the input component and the output, it is characterised in that the output has
It is axially toward the second radial direction of the first radial support section of input component extension, the first radial support section and input component
Support section corresponds to one heart.
The content of the invention
The present invention is based on following tasks, improves in structure and/or functionally the torsional vibration damper being initially mentioned.
The task solves by the torsional vibration damper of the feature with claim 1.
The torsional vibration damper can be used in being arranged in the drivetrain of motor vehicle.The drivetrain can have driving machine.Should
Driving machine can be internal combustion engine.The internal combustion engine can have bent axle.The drivetrain can have friction clutch device.The driving
System can have hydraulic torque converter.The drivetrain can have speed changer.The drivetrain be able to can drive with least one
Wheel.The drivetrain can have auxiliary unit drive device.Torsional vibration damper can implement into double mass flywheel.Torsional oscillation subtracts
The device that shakes can be arranged between driving machine and hydraulic torque converter or speed changer.
Term " input component " and " output " are related to from the conduction stream direction of driving machine.If not it is further noted that or
Do not draw other situation in this case, term " axial direction ", " radial direction " and be related to prolonging for pivot center " in circumferential direction "
Stretch direction.So " axial direction " corresponds to the bearing of trend of pivot center.So " radial direction " is perpendicular to pivot center bearing of trend
And the direction intersected with pivot center.So correspond to " in circumferential direction " around the circular arc direction of pivot center.
Spring assembly can have at least one machinery energy storage device.At least one machinery energy storage device can one
Aspect is supported on input component and is on the other hand supported on output.At least one machinery energy storage device can be spiral shell
Revolve spring.At least one machinery energy storage device can be compression spring.At least one machinery energy storage device can be
Semielliptic spring.The rubbing device can have at least one frictional disk.
Input component can have flange section.The flange section can be dish type.The flange section, which can have, carries footpath
To extension edge section and the l-shaped cross section of axially extending border area section.The axially extending border area section of the flange section can have
End.Input component can have cover region section.The cover region section can be annular.The cover region section can have radially outward edge.Should
Cover region section can have radially inward edge.The flange section and the cover region section can be fixedly connected to each other.The flange section and
The cover region section can mutually material be connected cohesively together, especially weld.The cover region section can be by its radially outward edge and the flange
Section connects.The flange section can be connected by the end of its axially extending border area section with the cover region section.The flange section and
The cover region section being capable of reception space of the gauge at least one machinery energy storage device.The reception space can have ring type shape
Shape.The input component, which can have, extend into support in the reception space, at least one machinery energy storage device
Section.The input component can have support sheet material.The support sheet material can be annular.The support sheet material can have outer straight
Footpath, the overall diameter is at least about corresponding to flange section and/or cover region section overall diameter.The support sheet material can have band
There is the l-shaped cross section of radially extending edges section and axially extending border area section.The axially extending border area section of the support sheet material can
With end.The support sheet material can be arranged in cover region section.The support sheet material can regularly connect with the cover region section
Connect.It is described support sheet material can with the cover region section force closure and/or shape sealed be connected, especially rivet.
The output can have flange part.The flange part can be arranged in the flange section and the cover region section in the axial direction
Between.The flange part can have to the raised of radially outer stretching.The projection can extend into the reception space.This is prominent
Rising can work as at least one machinery energy storage device, output side support section.The output can
With flywheel mass part.The flange part and the flywheel mass part can be fixedly connected to each other.The flange part and the flywheel mass
Part can mutually force closure and/or shape sealed connect, especially rivet.
The flywheel mass part at least can be arranged in by the cover region section section in the axial direction.The flywheel mass part can
At least it is arranged in the axial direction by the support sheet material section.The flywheel mass part can be at least substantially arranged in by the branch
In the reception space of fagging material gauge.The flywheel mass part can have radially outward edge.The flywheel mass part it is radially outside
Edge can have staged shape wide.The radially outward edge of the flywheel mass part at least can have radial surface section.This flies
The radially outward edge of wheel mass member at least can have axial surface section.The flywheel mass part can have towards the input
The side of part.Notch can be arranged on the side.The notch can be flute profile.The notch can be annular.
The supporting arrangement can act as the supporting arrangement that can mutually reverse of input component and output.The supporting arrangement
The pre-determined tilt position of the pivot center of input component and the pivot center of output can be realized.The supporting arrangement can have
At least one rolling bearing.The supporting arrangement can have at least one ball bearing.The supporting arrangement can have at least
One groove ball bearing.The supporting arrangement being capable of the groove ball bearing with the adaptation f that band is improved.The adaptation f
The business between guide rail radius and rolling element diameter can be provided.The supporting arrangement can have following groove ball bearings, and this is recessed
Groove ball bearing has fI>0.52 inner ring adaptation, especially f >=0.53, and/or fA>0.54 outer shroud adaptation, especially fA≥
0.55。
At least one first support section and at least one second support section being capable of gauge effect gaps.The effect gap
It can at least diminish in the axial direction of torsional vibration damper and/or in the case of tilting load rise section.From in input component and defeated
The pre-determined tilt angle gone out between part rises, at least one first support section and at least one second support section energy
It is enough at least to abut section.The pre-determined tilt angle can be about 0.2 ° to about 1 °, especially about 0.3 °
To about 0.6 °.It is described it is at least one first support section and it is described it is at least one second support section can diametrically with institute
State supporting arrangement and separate spacing as far as possible.At least one first support section and at least one second Support
Section can act as slanted gap limits device.
At least one first support section and at least one second support section can in radial directions extremely
It is disposed approximately in less in lid segments area.At least one first support section and at least one second support section energy
It is enough to be at least about arranged in radial directions in the radially outward edge region of the cover region section.At least one first support
Section and at least one second support section can be at least about arranged in radially inward edge region in radial directions.
At least one first support section and at least one second support section being capable of at least about cloth in radial directions
Put in rubbing device region.At least one first support section and at least one second support section can be in footpaths
At least it is disposed approximately in spring assembly region on to direction.At least one first support section and described at least one the
Two support sections can be arranged in the radial outside of the spring assembly.
For pivot center, at least one first support section can have the supporting surface of truncated cone shape first.Should
The supporting surface of truncated cone shape first can have supplement cone, and the tip of supplement cone is at least approximately at supporting arrangement on pivot center
In region.For pivot center, at least one second support section can have the supporting surface of truncated cone shape second.This section
The supporting surface of taper second can have supplement cone, and the tip of supplement cone is at least approximately at supporting arrangement area on pivot center
In domain.The effect gap can extend relative to pivot center and relative to the planar tilt perpendicular to pivot center.
The effect gap can be truncated cone shape.
At least one first support section can have the supporting surface of cylindricality first for pivot center.This first
Supporting surface can be inner face.At least one second support section can have cylindricality second to support for pivot center
Face.Second supporting surface can be outside.The effect gap can extend parallel to pivot center.The effect gap energy
Enough it is cylindricality.
At least one first support section can be arranged in cover region section.At least one first support section energy
Enough it is arranged on the radially inward edge of the cover region section.The cover region section can have at least one projection for pointing to flywheel mass part.
At least one projection can have ring type shape.At least one projection can manufacture with cover region section single type.It is described extremely
A few projection can have pillar support face.
At least one first support section can be arranged on support sheet material.At least one first support section
It can be arranged on the end of axially extending border area section of the support sheet material.The end of the axially extending border area section of the support sheet material
There can be the supporting surface of truncated cone shape.The end of the axially extending border area section of the support sheet material can have pillar support face.
At least one second support section can be arranged on flywheel mass part.At least one second Support
Section can be arranged on the radially outward edge of flywheel mass part.The radially outward edge of the flywheel mass part can have truncated cone shape branch
Support face.The radially outward edge of the flywheel mass part can have pillar support face.At least one second support section can
It is arranged on the side of flywheel mass part.At least one second support section can be arranged in the side of flywheel mass part
On notch.The side of the flywheel mass part can have pillar support face.
At least one first support section and/or at least one second support section can be adjusted.It is described
At least one first support section and/or at least one second support section can be formed by carrying bolt.The support
Bolt can have the bolt head for forming support section.The carrying bolt can be threaded into input component.The carrying bolt
It can be threaded into cover region section.The carrying bolt can be threaded into output.The carrying bolt can screw thread twist
Enter into flywheel mass part.
Ground and in other words is summarized, the groove ball of double mass flywheel and inclination and offset is especially obtained from there through the present invention
The slanted gap limiting structure (Kippspielbegrenzung) that bearing is combined.Can use with bracket panel exterior domain
The groove ball bearing for the inclination and offset that bracket panel additional support is combined, the additional support of the bracket panel is relative to double mass flywheel
Master.The bearing of inclination and offset ensures, it is determined that heeling moment in the angle of inclination that occurs it is sufficiently large, so as to simpler
Ground determines that gap is measured for slanted gap limits device with presenting tolerance.The support can not only in the axial direction but also diametrically
Realize.The slanted gap limiting structure is arranged to more remote from the run-on point of double mass flywheel bearing, then it is more effective.Tilt inclined
The bearing of shifting can have big adaptation ratio and be combined with slanted gap limits device.The support can be placed in
Realized between component and bracket panel on master or between the component and bracket panel of master.Angle of inclination limiting structure is from double matter
The tolerance that the bearing of amount flywheel disposes more remotely and gap amount in component is related is smaller, then angle of inclination limiting structure is got over
Effectively.Here, the sensing in slight taper gap is relative to Support Position and the bearing on whole double mass flywheel rotation axis
The connecting line of run-on point can be at a right angle.This arrangement only causes small tolerances to slanted gap limiting structure.Also can
The slanted gap limiting structure only diametrically acted on is realized, especially when effect of the bearing from slanted gap limits device is stitched
When the spacing of gap is big.
The load that supporting arrangement do not allow is avoided by according to the torsional vibration damper of the present invention.Subtract the load of supporting arrangement
It is small.Axial force and/or tilting force can be supported outside supporting arrangement.Improve the service life of supporting arrangement.Make operation
Security improves.Avoid cut-out pressure oval.The large-size of supporting arrangement can be cancelled.Larger installing space is not required.Limit
Expense processed, such as cost.The angle of inclination between input component and output that operation needs can be realized.In the axis of rolling
Rolling element is avoided not allow in holding axially displaced.The load for avoiding the seamed edge of radial side not allow in sliding bearing.Keep away
The deformation that output does not allow is exempted from.Reduce tolerances.Increase angle of inclination.Simplify for slanted gap limitation dress
Determine that gap is measured with being equipped with tolerance.
Brief description of the drawings
Embodiments of the invention are explained referring next to accompanying drawing.Further feature and advantage are obtained from the explanation.
The specific features of the embodiment can show which the general characteristic of the present invention.The feature combined with other features of the embodiment
Also it can show which each feature of the present invention.
It schematically and is exemplarily illustrated：
Fig. 1 has the double mass flywheel for the truncated cone shape supporting surface for being arranged in semielliptic spring radial outside,
The groove ball bearing of the adaptation being improved of Fig. 2 tool double mass flywheels,
The supporting surface of the truncated cone shape of Fig. 3 double mass flywheels,
Fig. 4 has the double mass flywheel in the pillar support face for being arranged in semielliptic spring radial outside,
Fig. 5 has the double mass flywheel in the pillar support face being arranged in rubbing device region, and
Fig. 6 has the double mass flywheel of carrying bolt.
Embodiment
Fig. 1 shows double mass flywheel 100.Double mass flywheel 100 is used to be arranged in internal combustion engine in the drivetrain of motor vehicle
Between friction clutch.Double mass flywheel 100 is used for the rotation inhomogeneities vibration damping in drivetrain.This kind of rotation is uneven
Property can be encouraged especially by internal combustion engine.
Double mass flywheel 100 has input component 102 and output 104 with common rotation axis 106.Input component 102
It can together rotate around pivot center 106 with output 104 and limitedly reverse relative to each other.Adaptation with raising
Single groove ball bearing 107 be used for the supporting that can mutually reverse of input component 102 and output 104.
Fig. 2 shows the detailed view of groove ball bearing 107.Groove ball bearing 107 has inner ring 140, outer shroud 142 and spheroid
(such as 144).Inner ring 140 is arranged on input component 102.Outer shroud 142 is arranged on output 104.Spheroid 144 has ball respectively
Body diameter DwRadius of sphericity r in other wordsw.Inner ring 140, which has, carries groove radius rIGroove, for spheroid 144.Outer shroud 142 has
Have and carry groove radius rAGroove, for spheroid 144.Groove radius rIWith groove radius rAIt is respectively relative to radius of sphericity rw
Increase in this wise so that the pivot center of inner ring 140 and the pivot center of outer shroud 142 relative to each other can angular movements.Groove radius
rIWith groove radius rASuch as respectively it is radius of sphericity rw110%.Thus adaptation f=0.55 is respectively obtained.
Input component 102 has flange section 108 and cover region section 110.Flange section 108 is dish type and has L-shaped horizontal
Section, the cross section have radially extending edges section and the axially extending border area section with end.The cover region section be annular and
And there is radially outward edge 112 and radially inward edge 114.The end of the axially extending border area section of flange section 108 and cover region section
110 radially outward edge 112 is fixedly connected to each other, and is currently weldering grounding connection.Flange section 108 and the gauge of cover region section 110
Anchor ring shape reception space 116.
Input component 102 has support sheet material 118.Support sheet material 118 is annular, is had outer straight with flange section 108
The overall diameter of footpath and/or cover region section 110 at least approximately corresponding overall diameter, and have and carry radially extending edges section and axle
To the l-shaped cross section of extension edge section, the axially extending border area section has end 120.Support sheet material 118 and cover region section 110
It is permanently connected.
Output 104 has flange part 122 and flywheel mass part 124.Flange part 122 and flywheel mass part 124 are mutually solid
Surely connect, be currently riveting grounding connection.Flywheel mass part 124 has shell-type shape.The section of flywheel mass part 124 in axial direction
On be arranged in support sheet material 118 by.The following reception spaces of the gauge of sheet material 118 are supported, flywheel mass part 124 is arranged in reception sky
In.Flywheel mass part 124 has the wide radially outward edge 126 of staged shape, and the radially outward edge has section radial direction
With the surface of section axial direction.
The truncated cone shape supporting surface of input component 102 is formed on the end 120 of the axially extending border area section of support sheet material 118
128.The corresponding truncated cone shape branch of output 104 is formed on the wide radially outward edge 126 of the staged shape of flywheel mass part 124
Support face 130.Fig. 3 shows the truncated cone shape supporting surface 128,130 of double mass flywheel 100.
Composition acts on gap 132 between supporting surface 128,130.Effect gap 132 has width a.Effect gap 132 exists
Reduce in the case that the axial load and/or inclination load of double mass flywheel 100 improve section.From in input component 102 and defeated
The pre-determined tilt angle gone out between part 104 rises, and abuts, so as to protect bearing 107 not supporting surface 128,130 sections
By excessive load.There is truncated cone shape supporting surface 128,130 supplement to bore, and the tip (such as 134) of supplement cone is in pivot center
It is axially located on 106 in the region of bearing 107.Effect gap 132 is truncated cone shape and extended simultaneously towards pivot center 106
And relative to the planar tilt perpendicular to pivot center.Holding 107 has axial distance b off axis in effect gap 132.
Spring damper works between input component 102 and output 104.The spring damper has with bow
The spring assembly of shape spring (such as 136).Semielliptic spring 136 is arranged in reception space 116.On the one hand semielliptic spring 136 props up
On the other hand support is supported on the flange part 122 of output 104 on the flange section 108 and cover region section 110 of input component 102.
The spring damper has the rubbing device with drag ring 138.The footpath that the rubbing device is arranged in cover region section 110 is inside
On edge 114.
Fig. 4 shows double mass flywheel 200, have be arranged in the radial outside of semielliptic spring 202 pillar support face 204,
206.Support sheet material 208 axially has radially inner face on extension edge section 210.First pillar support face 204 is inside in footpath
Side is arranged on the end 212 of the axially extending border area section 210 of support sheet material 208.Flywheel mass part 214 is in its radially outward edge
Have on 216 radially outside.Second pillar support face 206 is arranged on the edge 216 of flywheel mass part 214 in radial outside.
In addition, especially complementally referring to figs. 1 to Fig. 3 and affiliated explanation.
Fig. 5 shows double mass flywheel 300, have the pillar support face 304 in the region of rubbing device 302 of being arranged in,
306.Cover region section 308 has the annular projection 314 for pointing to flywheel mass part 312 on its radially inward edge 310, and the annular is dashed forward
Rising has radially inner face.First pillar support face 304 is arranged on the annular projection 314 of cover region section 308 in radially inner side.Flywheel
Mass member 312 has towards the side 316 of cover region section 308, and the side, which has, carries radially outside annular groove 318.Second
Pillar support face 306 is arranged on the groove 318 of flywheel mass part 312 in radial outside.In addition, especially complementally reference picture 1
To Fig. 3 and affiliated explanation.
Fig. 6 shows the double mass flywheel 400 with carrying bolt 402.Carrying bolt 402 is threaded into input component 406
Cover region section 404 in and there is bolt head, the bolt head is for being supported on flywheel mass part 408.Flywheel mass part 408
With the groove for the bolt head.Spacing between the bolt head and flywheel mass part 408 can be supported by screw-in/back-out
Bolt 402 adjusts.In addition, especially complementally referring to figs. 1 to Fig. 3 and affiliated explanation.
Reference numerals list
100 torsional vibration dampers, double mass flywheel
102 input components
104 outputs
106 pivot centers
107 supporting arrangements, groove ball bearing
108 flange sections
110 cover region sections
112 radially outward edges
114 radially inward edges
116 reception spaces
118 support sheet materials
120 ends
122 flange parts
124 flywheel mass parts
126 edges
128 first supporting surfaces
130 second supporting surfaces
132 effect gaps
134 tips
136 semielliptic springs
138 drag rings
140 inner ring
142 outer shrouds
144 spheroids
200 torsional vibration dampers, double mass flywheel
202 semielliptic springs
204 first supporting surfaces
206 second supporting surfaces
208 support sheet materials
210 border area sections
212 ends
214 flywheel mass parts
216 edges
300 torsional vibration dampers, double mass flywheel
302 rubbing devices
304 first supporting surfaces
306 second supporting surfaces
308 cover region sections
310 radially inward edges
312 flywheel mass parts
314 projections
316 sides
318 grooves
400 double mass flywheels
402 carrying bolts
404 cover region sections
406 input components
408 flywheel mass parts
Claims (10)
1. torsional vibration damper (100,200,300,400), especially double mass flywheel, the torsional vibration damper (100,200,
300th, 400) have：
- input component (102,406) and output (104) with common rotation axis (106), the output carry cover region section
(110,308,404), the input component (102,406) and the output (104) can turn together around the pivot center
Move and can limitedly reverse relative to each other,
- the supporting arrangement (107) that is arranged between the input component (102,406) and the output (104) and described defeated
Enter the spring damper to be worked between part (102,406) and the output (104),
Characterized in that, the supporting arrangement (107) can angular movement, and the input component (102,406) have be used for
At least one first support section being supported on the output (104), and the output (104) has for supporting
At least one second support section on the input component (102,406), wherein, the support section is mutually corresponding, described
Support section diametrically separates spacing with the supporting arrangement (107), and from the input component (102,406) and this is defeated
The pre-determined tilt angle gone out between part (104) works.
2. torsional vibration damper (100,200,300,400) according to claim 1, it is characterised in that the supporting arrangement
(107) the groove ball bearing with the adaptation f improved is included.
3. the torsional vibration damper (100,200,300) according at least one in above claim, it is characterised in that described
Supporting arrangement (107) has groove ball bearing, and the groove ball bearing has fI>0.52 inner ring adaptation, especially f >=0.53
Inner ring adaptation, and/or there is fA>0.54 outer shroud adaptation, especially fA>=0.55 outer shroud adaptation.
4. the torsional vibration damper (100) according at least one in claims 1 to 3, it is characterised in that on described turn
For shaft line (106), at least one first support section has the first supporting surface (128) of truncated cone shape, and described
At least one second support section has the second supporting surface (130) of truncated cone shape.
5. the torsional vibration damper (200,300) according at least one in claims 1 to 3, it is characterised in that on described
For pivot center, at least one first support section has a supporting surface of cylindricality first (204,304), and it is described at least
One second support section has the supporting surface of cylindricality second (206,306).
6. the torsional vibration damper (300) according at least one in above claim, it is characterised in that described at least one
First support section is arranged on the cover region section (308).
7. the torsional vibration damper (100,200) according at least one in above claim, it is characterised in that the input
Part (102) has support sheet material (118,208), and at least one first support section is arranged in the support sheet material
On (118,208).
8. the torsional vibration damper (100,200,300,400) according at least one in above claim, it is characterised in that
The output (104) has flywheel mass part (124,214,312,408), and at least one second support section cloth
Put on the flywheel mass part (124,214,312,408).
9. the torsional vibration damper (100,200,300) according at least one in above claim, it is characterised in that described
At least one first support section and/or at least one second support section can be adjusted.
10. the torsional vibration damper (100,200,300,400) according at least one in above claim, its feature exists
In at least one first support section and at least one second support section are at least about arranged in radial directions
In the region of the cover region section (110,308).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102016214712 | 2016-08-09 | ||
| DE102016214712.9 | 2016-08-09 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN107701656A true CN107701656A (en) | 2018-02-16 |
Family
ID=61018121
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710584860.8A Pending CN107701656A (en) | 2016-08-09 | 2017-07-18 | Torsional vibration damper |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN107701656A (en) |
| DE (1) | DE102017117853A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113906239A (en) * | 2019-06-06 | 2022-01-07 | 采埃孚股份公司 | Torque transmission device |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102017117976A1 (en) | 2016-09-01 | 2018-03-01 | Schaeffler Technologies AG & Co. KG | torsional vibration dampers |
| DE102018115185A1 (en) | 2018-06-25 | 2020-01-02 | Schaeffler Technologies AG & Co. KG | torsional vibration dampers |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101223380A (en) * | 2005-07-14 | 2008-07-16 | 卢克摩擦片和离合器两合公司 | Vibration damping unit, in particular a dual-mass flywheel |
| CN103122970A (en) * | 2011-11-17 | 2013-05-29 | 舍弗勒技术股份两合公司 | Torsional vibration damper |
| DE102013210492A1 (en) * | 2013-06-06 | 2014-12-11 | Schaeffler Technologies Gmbh & Co. Kg | torsional vibration dampers |
| KR101620210B1 (en) * | 2014-10-23 | 2016-05-12 | 주식회사평화발레오 | dual mass flywheel |
-
2017
- 2017-07-18 CN CN201710584860.8A patent/CN107701656A/en active Pending
- 2017-08-07 DE DE102017117853.8A patent/DE102017117853A1/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101223380A (en) * | 2005-07-14 | 2008-07-16 | 卢克摩擦片和离合器两合公司 | Vibration damping unit, in particular a dual-mass flywheel |
| CN103122970A (en) * | 2011-11-17 | 2013-05-29 | 舍弗勒技术股份两合公司 | Torsional vibration damper |
| DE102013210492A1 (en) * | 2013-06-06 | 2014-12-11 | Schaeffler Technologies Gmbh & Co. Kg | torsional vibration dampers |
| KR101620210B1 (en) * | 2014-10-23 | 2016-05-12 | 주식회사평화발레오 | dual mass flywheel |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113906239A (en) * | 2019-06-06 | 2022-01-07 | 采埃孚股份公司 | Torque transmission device |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102017117853A1 (en) | 2018-02-15 |
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