CN107023609A - For automobile clutch disk or the torsional vibration damper of double mass flywheel - Google Patents
For automobile clutch disk or the torsional vibration damper of double mass flywheel Download PDFInfo
- Publication number
- CN107023609A CN107023609A CN201610063636.XA CN201610063636A CN107023609A CN 107023609 A CN107023609 A CN 107023609A CN 201610063636 A CN201610063636 A CN 201610063636A CN 107023609 A CN107023609 A CN 107023609A
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- Prior art keywords
- pad
- disk
- torsional vibration
- vibration damper
- elastic
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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
- F16F15/10—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
- F16F15/129—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 characterised by friction-damping means
- F16F15/1292—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 characterised by friction-damping means characterised by arrangements for axially clamping or positioning or otherwise influencing the frictional plates
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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
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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
The present invention relates to a kind of torsional vibration damper, for automobile clutch disk or double mass flywheel.Torsional vibration damper includes at least two coaxial elements and damping system, damping system is used for the relative rotation for resisting coaxial elements, damping torque is produced during to be relatively rotated in coaxial elements, damping system includes pad, co-axial member included by elastic prestress part and coaxial elements, pad and elastic prestress part are disposed axially between co-axial member, elastic prestress part is axially disposed within the operation interval formed between pad and a co-axial member with certain working depth, to apply axial bias to pad, torsional vibration damper is characterised by, at least one in pad and one co-axial member be for the surface that is in contact with elastic prestress part be in the ramp-like surface with taper.
Description
Technical field
The present invention relates to particularly for automobile clutch disk or the torsional vibration damper of double mass flywheel.
Background technology
It is the filter before engine torque is delivered into gearbox by clutch in the transmission mechanism of motor vehicle
Torsional vibration damper, is generally integrated in clutch disk by the vibrations caused by motor vehicle engine aperiodicity, thus limitation active
The transmission of vibrations between axle such as internal-combustion engine machine crankshaft and driven shaft such as transmission input shaft.For example into the shake in gearbox
It is dynamic operationally to cause wherein especially not by desired concussion, noise or sound injury.
This torsional vibration damper can equally be provided to the double mass flywheel (DMF) of motor vehicle.
It is known that being included in this kind of torsional vibration damper in for automobile clutch disk in the range of restriction around public
The relatively turnable hub of pivot center, radial ringed drive disk and two damper disks, torsional vibration damper also include setting
The elastic machine of circumferential action type between damper disk and drive disk, in the window that is engaged in two damper disks and drive disk
Structure, hub is fixedly connected with drive disk unitary rotation, two damper disks be arranged on the both sides of drive disk radially and
It is permanently connected together each other.
Disk is used to be driven rotation as being furnished with the bent axle of the automotive internal combustion engines of transmission mechanism by driving shaft, and disk
Hub is used to couple with transmission input shaft.
In addition further to extenuate vibrations, reduction noise, shock absorber may also include damping system, and the damping system is set
Apply frictional resistance moment of torsion during for there is angular travel between damper disk, drive disk, hub between them.For example, ginseng
See prior art literature US-4697682-A (its Figure 10) and US-5016744-A (its Fig. 6), wherein US-4697682-A is hit by a bullet
Property packing ring 52 be sandwiched between with certain working clearance between friction and holding ring 51 and lead ring 12 ', and in US-5016744-A
In, elastic washer 47a is equally sandwiched between the thrust ring that side panel 13a is in contact with same drag ring 45a with certain working clearance
Between 49a.To this reference can be made to subsequent figures 1-2.Wherein with the pad of elastic washer abutting contact as rubbed and holding ring or pushing away
The contact surface of power ring is disposed as the form in plane.Well known, this pad in damping system be used for elastic washer and
Adjacent another component is fitted together with fixed distance, to form the work with certain working depth for elastic washer
Make interval, so as to cause elastic washer to be compressed to certain altitude to produce load in operation, due to the load and pad table
Face coefficient of friction, generates frictional damping.Pad thus effectively forms the main member of this damping system.
But another surface of pad that in operation, damping system is such as contacted with another component such as drive disk of clutch disk with
The time of wearing weares and teares, naturally it is also possible to be that another component such as damper disk of contact resilient packing ring weares and teares.And due to such as
The design of the contact surface with elastic washer of the planar formula of pad in US-4697682-A and US-5016744-A, completely
This abrasion can not be compensated, so that the working depth increase of elastic washer, then middle elastic washer stand under load is interval just
It can change, i.e., H1, H2 change.For example, it is assumed that whole component (pad 1, elastic washer 2 and support cushion
Another component 3 of circle) total wear extent is that Δ H (is that another component 3 for supporting elastic washer weares and teares here, its thickness is from A1
It is reduced to A2), then correspondingly in the case of this plane pad 1, the working depth of elastic washer is added from H1 to H2
Δ H (H2-H1=Δ H), for example, see Fig. 3.This working depth of elastic washer, which changes, causes its load to reduce so that produced
Raw active force will change, so as to ultimately result in damping large change.
This damping change influences whether the stability of damping system so that be transmitted to the increasing such as vibrations, noise of gearbox
Plus, so as to influence occupant comfort sexual experience.That is, this damping change causes damping stability is reduced and shortened to subtract
Shake the device life-span.
In fact, influenceing the stability of damping system generally related to motor vehicle noise has many factors, wherein especially
It is to include the load that for example elastic washer is produced, in fact, being sent out under different stand under load height by the power produced by elastic washer
Changing, also just changes therewith to the component pressure applied in its both sides.That is its abrasion and cushion with whole component
The loading force of circle itself is related.And the problem of solve related to this, then can improve foregoing stability.
The content of the invention
Based on this, the present invention is intended to provide a kind of torsional vibration damper, with product during use by occur abrasion up to
The increased working depth of elastic washer is partially compensated, so that the damping system stability of torsional vibration damper significantly increases
Plus, thus the life-span is longer.
In addition, the present invention also aims to the stabilization for the damping system for improving torsional vibration damper in a simple manner decoupled, at lower cost
Property.As described above, the loading force of control elastic washer in itself can improve this stability.A kind of mode is to improve cushion
The stability of circle itself.There is fatigue life in elastic washer, more than then its power can change after the life-span, produce decay.Improve bullet
Property packing ring material and processing as quenching, be tempered if can improve its stability.But this mode seems more complicated, cost is at present
It is not low.In contrast to this, the present invention is not based on this material and processing, but from this damping system of torsional vibration damper
The configuration aspects of structure, especially pad control the stability, thus mode by increasing the component of similar wear-compensating
Simpler, cost is relatively low.
Thus, the present invention proposes a kind of torsional vibration damper, and it includes：At least two coaxial elements, they are arranged to
It is pivotably movable with respect each other in the range of restriction, wherein each coaxial elements include a co-axial member；Damping system, it is same for resisting
The relative rotation of axle portion part, to be relatively rotated in coaxial elements during produce damping torque and absorb and slow down the non-of rotation
Periodicity and vibration, the damping system include the co-axial member included by pad, elastic prestress part and coaxial elements, pad
And elastic prestress part is disposed axially between co-axial member, and elastic prestress part is axially arranged with certain working clearance
In the operation interval formed between pad and one of co-axial member, with to pad apply axial bias, pad with it is described
One co-axial member can rotationally be connected at least a portion of the relative rotation range of restriction, it is characterised in that pad and
At least one in one co-axial member be for the surface that is in contact with elastic prestress part be in the ramped shaped with taper
Surface.
Advantageously, pad is damping fin, and damping fin also plays holding ring, and damping fin passes through elastic prestress part axle
To adjacent another co-axial member is pressed against, so as to exist between co-axial member when relatively rotating stroke by friction drive.
Advantageously, it is in the ramped shaped table with taper that the surface for direct contact resilient prestressed member of damping fin, which is,
Face.
Advantageously, pad is another annular construction member, another annular construction member formation holding ring, is plugged on elastic prestress
Between part and damping fin, damping fin is set axially to be pressed against adjacent another co-axial member by elastic prestress part and holding ring, from
And damping fin is existed between co-axial member when relatively rotating stroke by friction drive.
Advantageously, it is in the ramp-like surface with taper that the surface for contact resilient prestressed member of holding ring, which is,.
Advantageously, one co-axial member for the surface that is in contact with elastic prestress part in taper
Ramp-like surface.
Advantageously, the tapered construction of ramp-like surface is adapted into the shape with elastic prestress part and placement angle.
Advantageously, ramp-like surface is arranged to that for the outer or interior double wedge that its cone angle has positioned at elastic prestress part
On side so that as abrasion occurs, the outer or interior double wedge of elastic prestress part is along ramp-like surface and towards ramp-like surface thickness
Recover to the free shape of elastic prestress part in incremental direction.
Advantageously, elastic prestress part is in truncated cone shape, with outer or interior double wedge.
Advantageously, elastic prestress part is disk spring washer.
Advantageously, foregoing torsional vibration damper is used for automobile clutch disk, and the co-axial member of the coaxial elements includes
Hub, radial ringed drive disk and two damper disks, torsional vibration damper also include being engaged in two damper disks and drive
Circumferential action type elastic mechanism in window in Moving plate, hub is fixedly connected with drive disk unitary rotation, described two vibration dampings
In the both sides of drive disk radially, described two damper disks are permanently connected together and can be relative to device disk each other
Hub and drive disk are installed in which can rotate coaxially；Pad and the elastic prestress part is axially disposed within drive disk or hub and one
Between individual damper disk so that form pre- for elasticity between pad and one damper disk with certain working clearance
The operation interval of stress member, pad can turn with one damper disk at least a portion of the relative rotation range of restriction
It is connected dynamicly, the elastic prestress part applies axial bias to pad；Characterized in that, pad and one damper disk
In at least one be for the surface that is in contact with elastic prestress part be in the ramp-like surface with taper.
Advantageously, another co-axial member is drive disk.
Advantageously, the torsional vibration damper is additionally operable to motor vehicle double mass flywheel.
Brief description of the drawings
By read referring to the drawings with non-limiting example carry out it is described below, the present invention will be better understood when and this
Other details, the feature and advantage of invention will be embodied, in accompanying drawing：
- Fig. 1 and Fig. 2 is two kinds of plane pads of the torsion vibration damper system described above according to prior art
Circle；
- Fig. 3 schematically shows that elastic washer work is high under the plane packing ring described above using prior art
The change of degree；
- Fig. 4 shows schematically the elastic washer under using the slope type packing ring with taper according to the present invention and worked
The change of height；
- Fig. 5 represents the perspective exploded view of automobile clutch disk；
- Fig. 6 schematically shows the axial section of the automobile clutch disk after the assembling of prior art；
- Fig. 7 is the enlarged detail portions figure for representing the signified positions of circle X in Fig. 6；
Two kinds of elastic washers with interior double wedge and with outer double wedge are shown respectively in-Fig. 8 and Fig. 9；
- Figure 10 and Figure 11 illustrate two kinds of damping fins 11 ' and 12 ' according to prior art with perspective respectively；
- Figure 12 is schematically shown after the change according to the present invention for the square frame C in Fig. 7 according to prior art
The view of the part；
- Figure 13 is schematically shown after the change according to the present invention for the square frame D in Fig. 7 according to prior art
The view of the part；
- Figure 14 is the axial section of another automobile clutch disk of the prior art similar to Fig. 6；
The circle E that-Figure 15 a represent in Figure 14 represents the enlarged diagram at position, Figure 15 a and 15b then by test with than
Shown compared with mode under the same conditions using the plane pad of prior art with being obtained according to the ramped shaped pad of the present invention
The Different Results obtained.
Embodiment
In the present specification and claims, using term " outer (portion) " and " interior (portion) " and " axial direction " and " radial direction "
Direction indicates clutch disk component to be used without limitation according to the definition provided in specification.Generally, " radial direction " direction is being just
Meet at the pivot center A of clutch disk and be orientated from inside to outside away from the rotational axis x, wherein rotational axis x determines " axle
To " direction, " circumference " direction is orthogonal to the pivot center A of clutch disk and is orientated with being orthogonal to radial direction.Term is " outer
(portion) " and " interior (portion) " be used to limit relative position of the component relative to another component with reference to the pivot center A,
Accordingly, with respect to the external member for being located radially at periphery, the component close to axis is referred to as internals.In addition, term
" rear " and " preceding " be used to limit relative position of the component relative to another component in axial direction, for being arranged in hair
Component near motivation is indicated by " rear ", is indicated for being arranged in the component near speed changer by " preceding ".Term is " radially
Positioned at " refer to being located normal in the plane of axis X and with axis X at a distance of the radial distance determined.
As it was previously stated, clutch disk is used to be arranged in the driving-chain of motor vehicles, positioned at engine and speed changer
Between.This frictional disk is mounted to rotationally be fixedly connected with the input shaft of speed changer, positioned at the pressing plate and reaction plate of clutch
Between and be fixedly connected with the crank rotation of internal combustion engine.When carrying out bonding operation, pressing plate makes frictional disk be pressed from both sides against reaction plate
Hold, torque is thus transmitted from bent axle to the input shaft of speed changer.
Referring to Fig. 5, wherein having the automobile clutch friction with torsional vibration damper in technology with decomposition diagram
Dish structure.Wherein, two friction facings 1,1 ' on the left of figure are fixed for example on two surfaces of metal supporting disk 2
In all edges of supporting disk, for example, passed through by multiple rivets 3 (referring to Fig. 6) and be correspondingly disposed in friction facing and its supporting disk
Friction facing is fixed on the both sides of supporting disk by the perforate of respective radially aligned.In this example, friction facing supporting disk is progressive
Disk, also known as corrugated sheet.
Supporting disk 2 is fixed on two damper disks 5,5 ' that axially-spaced and by such as rivet 4 fixture is fixedly connected with.
And drive disk 6 is axially disposed between two damper disks 5,5 '.Hub 7 with drive disk 6 resist at an angle by clearance
Elastic mechanism can rotationally be connected together.
Supporting disk 2 with friction facing 1,1 ' and two components formed of shock absorber 5,5 ' and the drive being fixedly connected with hub 7
Moving plate 6 resists the effect of elastic mechanism 8 and surrounds relative angular displacement models of the common axis A in predetermined limits relative to each other
Enclose interior rotation.
It is torsional vibration damper used herein of shock absorber, includes the elastic mechanism 8 of circumferential action type, elastic mechanism 8 is common
Ground is by the spiral shape bullet of the main shaft with circumferential direction circumferentially in series between drive disk 6 and damper disk 5,5 '
Spring is formed.Specifically, drive disk 6 is more with being axially aligned formed with along along part in damper disk 5,5 ', in its respective week
Individual window, there is four windows 51,5 ' 1,61 respectively here.These windows are separated by radial direction pawl.In addition in friction facing supporting disk 2
Be again provided with along along the radial inside portion in region for receiving elastic mechanism the relative week for fixed friction liner
The groove 21 of end axial component, is here four grooves.Therefore these windows and groove radially aligned and formed for receiving
The seat slot of elastic mechanism, elastic mechanism is held therein to prevent from axially deviating from from window.
Further, separated between four grooves 21 of friction facing supporting disk by inwardly protruded four tongue pieces 22,
Have on each tongue piece for fixing rivet by hole 23, this some holes 23 is located at window for same two damper disks during assembling
Hole 52 between mouthful, 5 ' 2 and axially aligned with the elongate holes 62 between the window of drive disk, to form such as rivet 4
The passage that fixture passes through, the supporting disk and damper disk, drive disk that thus will be equipped with friction facing is circumferentially rotated with certain
Clearance can be rotationally locked together.To this reference can be made to the latter half of axial section shown in Fig. 6.
The component and drive disk are fitted in hub 7 by its central aperture, and axis A constitutes the central axial line of hub.
Hub carries hoop 71 on outside, and hoop has flange 72.The thickness of hoop periodically reduces, to form outer denture.
The outer denture of hoop is suitable to the interior denture 63 with drive disk 6 by engaging cooperation.
Other torsional vibration damper also includes damping system, for prevent the relative motion between drive disk and damper disk with
Further slow down vibrations.
Be towards engine side on the left of Fig. 7 on, the radial inner portion for the damper disk 5 being fixed together with supporting disk
Axially gear is against the one side of hub flange, and damping fin 11 is plugged between damper disk 5 and the side of flange 72, hinders
Adjust pad 16 has alternatively been may also set up between Buddhist nun's piece 11 and the side of hub flange.And as clearly shown in Figure 7, for
Damper disk 5, its radial inner portion is contacted and the axially-extending portion of damping fin 11 with the radially extending portion 112 of damping fin 11
The recess 5a of formation in the inner edge part of point (protruding pin) 11a insertion damper disk 5 and connect together, and the axle of damping fin 11
Extend to extension 11a along the hub peripheral, axial part of the retraction vertical with flange.Similarly, in the opposite side of flange
Side is to be provided with possible same adjust pad 16 ', damping fin 11 ' and damper disk in succession towards on the direction of gearbox
5’.But unlike, keep certain workplace unoccupied place to be provided with elasticity between the damping fin 11 ' and damper disk 5 ' and in advance should
Power part, such as elastic washer 13, elastic washer is preferably disk spring washer, or wavy spring.
Referring to Fig. 8 and 9, wherein two kinds of elastic washers with interior double wedge and with outer double wedge are shown respectively.
In Fig. 6-7, elastic washer 13 is band convex flute profile, the annular, radially extending portion of its interior double wedge and damping fin 11 '
The projection formed in 11 ' a is divided to be engaged connected to realize.The b of axial continuation (protruding pin) 11 ' insertions of damping fin 11 ' subtract
Shake the formation in the inner edge part of device disk 5 ' the d of recess 5 ' and connect together.As shown in fig. 7, damper disk 5 ' has radially
The interior a of part 5 ', the radially outer staggered axially backward point 5 ' c, are linked together by the b of bending part 5 ' between them, and are somebody's turn to do
The other end of elastic washer 13 be external toroidal ring part only need to simply rest on a of radially inner portion 5 ' of damper disk 5 ' with it is curved
At or near turning between 5 ' c of folding part point.As modification, groove can also be set on damper disk with positioning elastic
Packing ring.
In addition, also can be observed in the figure 7, damping fin 12 ' and for applying the elastic washer 14 of elastic prestress by axle
It is plugged on to ground between damper disk 5 ' and drive disk 6.And elastic prestress part is preferably again disk spring washer here,
Can be wavy spring, for elastic load to be put on into damping fin 12 ', elastic washer for example divides and multiple with circumferential lateral surface
Double wedge is simply resisted against the c of part 5 ' of damper disk 5 ' in its end in double wedge in the radial direction inwardly protruded out, these radial directions
On.And the top gear of the circumferential lateral surface of elastic washer point leans against a of inner radial portion 12 ' of damping fin 12 ' and axially extending portion
Divide at or near the turning between 12 ' b, the axially extending part such as b of protruding pin 12 ' is used for the c of part 5 ' for inserting damper disk 5 '
Formed in the e of recess 5 ' in.More properly, referring to exploded view 5, damping fin 12 ' has protruding pin, as shown in Figure 5 with four
The individual b of protruding pin 12 ', they are circumferentially distributed and are joined in the e of recess 5 ' formed in damper disk 5 '.By these protruding pins, elasticity
Packing ring is plugged on rotationally and away from ground the work formed between damper disk 5 ' and damping fin 12 ' with certain workplace
In interval, to ensure the thrust for promoting damping fin 2 against drive disk.
Additionally as modification, in the opening that the interior double wedge of elastic washer is correspondingly formed in being also embedded at damper disk.
Damping fin 12 ' contacted with drive disk be referred to as on the apparent surface 12 ' 1 of rubbing surface, when relatively rotating
When, the rubbing surface weares and teares.And elastic washer applies the damping fin surface 12 ' 2 of elastic prestress thereon and is referred to alternatively as applying
Plus face.As elucidated before, the application face is plane.
Alternatively, axially arranged there can be hold-down ring between damping fin 12 ' and elastic washer 14, by the non-company of elastic washer
The continuous power applied is distributed in damping fin.And herein, damping fin is integrated with the function of hold-down ring in itself.Damping fin 12 ' is now
Then it is directly pressed against by the elastic washer on drive disk.
It is being towards in engine side, similarly, damping fin 12 to be provided between damper disk 5 and drive disk 6 backwards,
And the damping fin 12 is joined in the corresponding recess of damper disk 5 again by protruding pin and is fixedly connected with each other, but in damping
The elastic washer such as disk spring washer is not provided between piece 12 and damper disk 5.Thus as clearly illustrated, vibration damping
The outer radial portion 5c of device disk 5 is in contact with the inner radial portion 12a of damping fin 12.
When there is relative rotation stroke between drive disk 6 and damper disk 5 ', damping fin 12 ' can be relative to damper disk
5 are driven rotation.As previously mentioned, it is rubbing surface generally on two surface according to the damping fin 11 ' and 12 ' of prior art
Flat shape is designed to application face, thus because abrasion occurs for such as damping fin rubbing surface and causes when can not compensate work
Elastic washer operation interval axial distance (also known as working depth) any change so that final damping change and shadow
Ring the stability to system.Referring to Figure 10 and 11, wherein two kinds of damping fins 11 ' and 12 ' according to prior art are shown respectively.
And the present invention can make up drawbacks described above.Therefore, according to the present invention, by damping fin 11 ' and/or 12 ' and elasticity
The application face of washer contacts is designed to the ramped shaped with taper.Utilize this taper of elastic washer so that damping fin is in difference
Region has continuous different thickness.When being worn and torn after damping system use, the working depth increase of elastic washer, elasticity
The top contacted with damping fin of the packing ring such as form in fingers, which is squeezed, to be reduced and causes to flick at the top of it.Due to damping fin
Taper, the height that elastic washer is flicked will at least in part be compensated by by the increased height of damping fin.Thus compared with plane
Type damping fin, is more stablized using the working depth of this elastic washer with taper, so as to cause to damp more stable, the product longevity
Life also extends.
For the square frame C in Fig. 7 by prior art, for example, see the part after the change represented according to the present invention
Figure 12.In Figure 12 according to the present invention, unlike the prior art, the application face 15a of damping fin 15 thickness from it is embedding
Entering radial inward at or near the intersecting turning of protruding pin of damper disk 5 ' gradually increases to form inclined domatic, correspondingly
Using the elastic washer 2 with outer double wedge rather than with interior double wedge with matched so that the outer double wedge of elastic washer blocks when initial
It is fixed at or near the turning.
As supplement or independently, such as (Figure 17 square frame D) may also set up this between hub and damper disk 5 '
Damping system with slope structure.Can be further referring to Figure 13 according to the present invention to this.Here, the application of damping fin 17
Face 17a thickness radially gradually increases at or near the turning that the protruding pin with embedded damper disk 5 ' intersects and forms one
The slope of taper is determined, here still using the elastic washer 2 with interior double wedge with matched so that the outer double wedge of elastic washer exists
It is fastened in when initial at or near the turning.
But it need to remind, above design is simultaneously nonrestrictive.In fact, the cone of ramped shaped pad such as damping fin 15,17
Angle is adjusted generally according to the design of elastic washer, and being generally located in elastic washer has the side of double wedge.That is, cushion
Remain to apply to contact at the thinner thickness in face with the slope shape of damping fin when the double wedge of circle is initial and be connected.The slope shape of pad
The thicker side on surface is on the direction that the double wedge of damping spring recovers to its free shape.
During operation, no matter clutch disk forward direction i.e. from engine to gearbox direction (matter) or it is reverse i.e. from
Gearbox is relatively rotated to engine direction (deceleration), and the drive disk that damping fin is for example rotated, which drives, to be rotated and its rubbing surface hair
Raw abrasion.Using the slope type damping fin according to the present invention, elastic washer 18 is gradually towards thicker direction, here edge during abrasion
The radial inward movement of application face, the increased working depth of elastic washer 14 is compensate for using tapered portion so that the damping system
System is more stablized.
If being also provided with the damping system of same type, when wearing and tearing, elastic washer between hub 7 and damper disk 5 '
Then radially, i.e. moved along the application face of damping fin 13 towards the increased direction of thickness, to realize and above similar function.Should
Damping system is the primary pre- vibration insulating system in the case where moment of torsion is smaller such as idling mode.And the damping between drive disk and damper disk
System is that participation is acted on when moment of torsion is larger.
For example, see Fig. 4 of the damping system according to the present invention, it is assumed that pad (damping fin) 1, elastic washer 2 and another
The total abrasion for the damping system that bearing member (damper disk) 3 is constituted together is all equally Δ H, but utilize the foregoing taper of liner, bullet
Property washer height become and turn to H2'-H1=Δ H- Δs L, it means that the small Δ L of wear extent.In other words, put down compared with presently used
Face type pad, the damping system life-span is then longer, and life amount is then Δ L/ Δ H x100%.
Under conditions of other conditions all same, the taper angle of pad such as damping fin will have influence on Δ L values.And no matter bullet
Property packing ring there is interior double wedge or outer double wedge, this new liner can be applicable.
Figure 15 a and Figure 15 b are showed schematically out under same experimental conditions, are utilized respectively existing plane pad and root
The different parameters such as elasticity realized according to the slope type pad with 15 ° of taper of the present invention under new state and worn-out state
The change of packing ring working depth and angle (elastic washer operating position) and elastic washer life-span etc..
From the figure and upper table it can be seen that, for it is new no matter the pad of the plastic material of plane or slope type
12 ', the axial distance D between the contact surface of elastic washer of its rubbing surface and damper disk 5 ' is 5.1mm；Elastic washer
Length l1, l2 be 8.4mm, working depth h1, h2 for the elastic washer 14,18 being plugged between pad and damper disk
(in the new pad with taper, elastic washer be resisted against slope close to thickness minimum locate, h2 thus be pad thinnest part and
The axial distance between the contact surface of elastic washer of damper disk) and the relative damper disk 5 ' of elastic washer angle of inclination
α 1, α 2 are 3.0mm and 16.63 ° respectively.In the situation for all occurring 0.5mm abrasions same with the pad of the CONTACT WITH FRICTION of drive disk 6
Under (wherein new plane spacer thickness e1 is 2.1mm, and the minimum thickness e2 of new slope type pad is 1.8mm), then
Thickness e ' 1 item of plane pad after abrasion is 1.6mm, and the minimum thickness e ' 2 of the slope type pad after wearing and tearing is
1.3mm.And after wearing and tearing, the axial distance D between pad friction face and damper disk keeps constant, i.e., still it is 5.1mm.But
For the plane pad for the 0.5mm that weares and teares, the working depth of elastic washer is changed into 3.5mm (h ' 1) from 3mm, that is, added
0.5mm；And for the slope type pad for the 0.5mm that weares and teares, the working depth of elastic washer is then changed into 3.45mm (h ' 2) from 3mm,
It merely add 0.45mm；And corresponding tilt angle alpha ' 1, α ' 2 are changed into 20.28 ° and 19.92 ° respectively.Then equally wearing and tearing
Under, for the pad with slope, the elastic washer life-span increased to 1.1 years from 1 year.Naturally (the damping of this Novel gasket is utilized
Piece), the torsional vibration damper service life extension with this damping system, use cost is accordingly reduced.
Pad such as damping fin is generally made up of plastics, nylon or metal material, and different materials have different friction systems,
It is specifically chosen as needed.And elastic washer is generally made up of high-carbon steel, its hardness is higher than the hardness of damping fin.
In this manual, as described before, with towards gearbox side be forward between drive disk and damper disk
Damping fin and elastic washer exemplified by illustrate, wherein, ramp-like surface is application face for example by casting or machining
Mode integrate on damping fin.But it is noted here that the present invention is not limited thereto.For example, as it was previously stated, can be with
Aforementioned holding ring is set between the damping fin and elastic washer, ramp-like surface can be integrated in the holding ring with
On the surface of elastic washer contact；Such as, can also be by such ramped shaped table if the shape and structure of damper disk is adapted to
Implement on the surface contacted with elastic washer of damper disk in face.Or, this damping structure with ramped shaped component is also
Can be integrated in the side towards engine of torsional vibration damper i.e. backwards on, for example damper disk 5 and with its respectively in connection with
Similar disk spring washer is set between damping fin 11 or 12, at least one of damper disk and damping fin and cushion
This ramp-like surface with taper is set on the surface for enclosing contact.In other words, in produce operation interval for elastic washer two
It can be designed with this ramp-like surface at least one of individual component.
In addition in fact, existing pad is also to have different diversified forms in fact in damping system, and referring in Figure 10
With 11 in show two kinds damping sheet forms.Regardless of whether be the pad such as damping fin of which kind of form, according to the present invention, as long as by its
The application face contacted with elastic washer is designed to that band has the slope of certain taper.
Although it is noted that the plane pad on prior art provided above and the slope according to the present invention
The design parameter example of the damping system of face type pad, but this is entirely nonrestrictive.In fact, the slope of slope type pad
Size is spent for example depending on the form of elastic washer, placement angle.When those skilled in the art completely can be according to specific design
Specific requirement come design pad for example damping fin apply face specific taper.For example, some elastic washers are than shallower, then pad
Cone angle can not be too big, to avoid packing ring most first meeting from passing through its interlude contact pins.On the contrary, some elastic washers are sharper
Suddenly, then the taper in pad application face can be with larger.Anyway, installation gradient phase of the taper of slope generally with elastic washer
Matching.
Certainly, the present invention is not limited to above description.Those skilled in the art can be in appended claims below
Many implementation modifications are obtained in the scope of the invention defined in book.
Claims (13)
1. a kind of torsional vibration damper, it includes：At least two coaxial elements, they are arranged in the range of restriction relative to that
This is rotated, wherein each coaxial elements include a co-axial member (5,5 '；6；7)；Damping system (12 ', 14,5 '；11’、13、
5 '), for resisting the relative rotations of coaxial elements, to be relatively rotated in coaxial elements during damping torque is produced to absorb
With the aperiodicity and vibration for slowing down rotation, the damping system includes pad (12 ', 11 '), elastic prestress part (14,13)
With co-axial member (5 ', 6；5 ', 7), pad and elastic prestress part are disposed axially between co-axial member, and elastic prestress
Part is axially disposed within the operation interval formed between pad and one of co-axial member (5 ') with certain working clearance, with
To pad (12 ', 11 ') apply axial bias, the relative rotation range of pad and one co-axial member (5 ') in restriction
Can rotationally it be connected at least a portion,
Characterized in that, at least one in pad (12 ', 11 ') and one co-axial member (5 ') be used in advance should with elastic
It is in the ramp-like surface with taper that the surface that power part (14,13) is in contact, which is,.
2. torsional vibration damper according to claim 1, it is characterised in that pad is damping fin, damping fin also plays holding ring
Effect, damping fin is axially pressed against adjacent another co-axial member by elastic prestress part, so as to be deposited between co-axial member
Driven when relatively rotating stroke by friction.
3. torsional vibration damper according to claim 2, it is characterised in that damping fin is used for direct contact resilient prestressing force
It is in the ramp-like surface with taper that the surface of part, which is,.
4. torsional vibration damper according to claim 1, it is characterised in that pad is another annular construction member, another annular
Component formation holding ring, is plugged between elastic prestress part and damping fin, makes damping by elastic prestress part and holding ring
Piece is axially pressed against adjacent another co-axial member, is rubbed so that damping fin exists between co-axial member when relatively rotating stroke
Wipe and drive.
5. torsional vibration damper according to claim 4, it is characterised in that holding ring is used for contact resilient prestressed member
It is in the ramp-like surface with taper that surface, which is,.
6. torsional vibration damper according to any one of claim 1 to 5, it is characterised in that one co-axial member
It is in the ramp-like surface with taper that surface for being in contact with elastic prestress part, which is,.
7. torsional vibration damper according to any one of the preceding claims, it is characterised in that the taper structure of ramp-like surface
Cause to be adapted with the shape and placement angle of elastic prestress part.
8. torsional vibration damper according to any one of the preceding claims, it is characterised in that ramp-like surface is arranged to it
Cone angle is located on that side for the outer or interior double wedge that elastic prestress part has so that as abrasion occurs, elastic prestress part
Outer or interior double wedge along ramp-like surface and towards the incremental direction of ramp-like surface thickness to the free shape of elastic prestress part
Recover.
9. torsional vibration damper according to any one of the preceding claims, it is characterised in that elastic prestress part is in truncated cone
Shape, with outer or interior double wedge.
10. torsional vibration damper according to claim 8, it is characterised in that elastic prestress part is disk spring washer.
11. torsional vibration damper according to any one of the preceding claims, for automobile clutch disk, the same to axle portion
The co-axial member of part includes hub (7), radial ringed drive disk (6) and two damper disks (5,5 '), torsional vibration damper
Also include the circumferential action type elastic mechanism being engaged in the window in two damper disks and drive disk, hub (7) and driving
Be fixedly connected with to disk (6) unitary rotation, described two damper disks (5,5 ') in the both sides of drive disk (6) radially, it is described
Two damper disks are permanently connected together and can pacified with rotating coaxially relative to hub (7) and drive disk (6) each other
Dress；The pad (12 ', 11 ') and elastic prestress part (14,13) are axially disposed within drive disk (6) or hub (7) subtracts with one
Shake between device disk (5 ') so that form pre- for elasticity between pad and one damper disk with certain working clearance
The operation interval of stress member (14,13), at least one of relative rotation range in restriction of pad and one damper disk
Can rotationally it be connected on point, the elastic prestress part applies axial bias to pad；Characterized in that, pad and one
At least one in damper disk be for the surface that is in contact with elastic prestress part be in the ramp-like surface with taper.
12. torsional vibration damper according to any one of the preceding claims, it is characterised in that another co-axial member is driving
Disk.
13. torsional vibration damper according to any one of claim 1 to 10, it is characterised in that the torsional vibration damper is also
For motor vehicle double mass flywheel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610063636.XA CN107023609A (en) | 2016-01-29 | 2016-01-29 | For automobile clutch disk or the torsional vibration damper of double mass flywheel |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610063636.XA CN107023609A (en) | 2016-01-29 | 2016-01-29 | For automobile clutch disk or the torsional vibration damper of double mass flywheel |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN107023609A true CN107023609A (en) | 2017-08-08 |
Family
ID=59524754
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610063636.XA Pending CN107023609A (en) | 2016-01-29 | 2016-01-29 | For automobile clutch disk or the torsional vibration damper of double mass flywheel |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN107023609A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108119607A (en) * | 2017-12-22 | 2018-06-05 | 宁波宏协股份有限公司 | Flywheel vibration absorber internal damping structure |
| CN110145553A (en) * | 2018-02-12 | 2019-08-20 | 舍弗勒技术股份两合公司 | Clutch driven plate and clutch |
| CN110382906A (en) * | 2017-03-17 | 2019-10-25 | 法雷奥离合器公司 | Clutch disk with friction washer |
| WO2020057384A1 (en) * | 2018-09-20 | 2020-03-26 | 台州赫兹电气有限公司 | Vibration-damping transmission coupling device for electromagnetic power-losing brake |
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|---|---|---|---|---|
| CN1191595A (en) * | 1995-03-21 | 1998-08-26 | 机动车产品股份有限公司 | Twin mass flywheel friction damping device |
| CN1945050A (en) * | 2005-08-31 | 2007-04-11 | Valeo离合器公司 | A friction clutch for a motor vehicle, and a pre-assembled module for such a friction clutch |
| CN101354064A (en) * | 2007-07-25 | 2009-01-28 | 卢克摩擦片和离合器两合公司 | Coupling device |
| WO2015140437A2 (en) * | 2014-03-20 | 2015-09-24 | Valeo Embrayages | Clutch device, in particular for a motor vehicle |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1191595A (en) * | 1995-03-21 | 1998-08-26 | 机动车产品股份有限公司 | Twin mass flywheel friction damping device |
| CN1945050A (en) * | 2005-08-31 | 2007-04-11 | Valeo离合器公司 | A friction clutch for a motor vehicle, and a pre-assembled module for such a friction clutch |
| CN101354064A (en) * | 2007-07-25 | 2009-01-28 | 卢克摩擦片和离合器两合公司 | Coupling device |
| WO2015140437A2 (en) * | 2014-03-20 | 2015-09-24 | Valeo Embrayages | Clutch device, in particular for a motor vehicle |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110382906A (en) * | 2017-03-17 | 2019-10-25 | 法雷奥离合器公司 | Clutch disk with friction washer |
| CN110382906B (en) * | 2017-03-17 | 2021-12-28 | 法雷奥离合器公司 | Clutch disc with friction washer |
| CN108119607A (en) * | 2017-12-22 | 2018-06-05 | 宁波宏协股份有限公司 | Flywheel vibration absorber internal damping structure |
| CN110145553A (en) * | 2018-02-12 | 2019-08-20 | 舍弗勒技术股份两合公司 | Clutch driven plate and clutch |
| WO2020057384A1 (en) * | 2018-09-20 | 2020-03-26 | 台州赫兹电气有限公司 | Vibration-damping transmission coupling device for electromagnetic power-losing brake |
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