CN1727723A - Torsional vibration damper - Google Patents
Torsional vibration damper Download PDFInfo
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- CN1727723A CN1727723A CN 200510091081 CN200510091081A CN1727723A CN 1727723 A CN1727723 A CN 1727723A CN 200510091081 CN200510091081 CN 200510091081 CN 200510091081 A CN200510091081 A CN 200510091081A CN 1727723 A CN1727723 A CN 1727723A
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- torsional vibration
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Abstract
The invention relates to a torsional vibration damper with an input component and an output component which can resist the effect of a plurality of energy storage devices between them with mutual torsion, wherein these energy storage devices are provided with at least one compressible spiral spring essentially arranged in the circumferential direction of the damper. Besides, one of the components bears at least one lever element swingable in circumferential direction, and at least when the input component and the output component are torsional with each other, the spiral spring can support the lever element with one end in the circumferential direction, so that the lever element can relatively bear the component swing.
Description
Technical field
The present invention relates to have the torsional vibration damper of an input block and an output block, input block and output block can be resisted the effect of some energy storage devices that work and reverse each other between them, wherein these energy storage devices have the compressible helical spring at least one circumferencial direction that is arranged on vibration damper basically, in addition, by one in these parts at least one lever piece that can swing in a circumferential direction of carrying, wherein at least between input block and output block during relative reversing, helical spring can be supported on in the end of its circumferencial direction on this lever piece in this wise, so that makes lever piece carry its parts swing relatively owing to reversing relatively.
Background technique
The torsional vibration damper that begins described type is for example proposed by DE 4433467Al and DE10119878A1.In these applications, give and described prior art, in these prior aries, also can use configuration of the present invention.
The invention task
Task of the present invention is, the torsional vibration damper of splitting the described type of initial portion is being further improved aspect damping behavior and the operating life, thus the interference noise that undesirable torsional vibration and can avoiding to a great extent causes thus in the filtering power train better in all working state of internal-combustion engine or Motor Vehicle.In addition, torsional vibration damper constructed according to the invention also can be made in simple and economic especially mode.
According to the present invention, this task is implemented in this wise: have some profiles with coefficient at least one lever piece of helical spring end regions, these profiles are arranged on corresponding profile acting in conjunction in this wise on the helical spring end with some, thus helical spring at least one end section lever piece during the circumferencial direction deflection against act on that centrifugal force ground on this spring section is stopped diametrically or quilt to pushing back.Therefore at lever piece between shaking peroid or because the swing of lever piece, corresponding spring end is supported diametrically and is stopped, can avoid thus:, undesirable strong friction on the supporting surface of radially outer, occurs owing to the centrifugal force that acts on this respective end portions section.Therefore the so relatively supporting surface in some zones of the end of this corresponding spring or helical spring at least end section is blocked in other words and is lifted diametrically.Guaranteed thus: in fact helical spring at least some end rings do not produce frictionally and can deform on certain speed range.
These profiles of lever piece can directly be molded on this lever piece, but or can be made of parts additional, that carried by its.The corresponding profile that is located on the helical spring end also can directly constitute by helical spring circle, but or by an additional parts formation that is located on the helical spring respective end portions, if necessary, be received in regularly on this end seeing on the helical spring axial direction.The latter for example can be by sealed assurance of shape between at least one circle of corresponding part and spring end, and this circle can be configured to clamping linkage structure (Schnappverbindung).
What meet the requirements especially is that lever piece constitutes by the spring part that is configured to bending deflection beam (Biegebalken) form.The spring part of this bending deflection beam shape can for example be used to load helical spring flange plate with other parts and constitute one.
Lever piece is supported on the input block and/or output block of torsional vibration damper swingably.Lever piece also can constitute independent parts in this configuration.What meet the requirements in the case is that an additional or independent energy storage device applies swing resistance or the torsional resistance that is used for lever piece.Lever piece is compacted in this wise by energy storage device thus, so that its supporting zone that is used for the corresponding spring end is extruded on the direction of this spring end.
Input block or output block can be in an advantageous manner be made of the parts of flange plate form, and these parts are carrying at least one lever piece.
Can guarantee by configuration according to the present invention: by connecting using that lever piece produces at the torsional resistance between input block and the output block and the helical spring that between them, works equally.
Helical spring can extend in an advantageous manner on the circumferencial direction of torsional vibration damper and produce a friction relevant with centrifugal force, in parallel with helical spring spring action in that torsional vibration damper is inner, thus, the dynamic torsional resistance that produces altogether by helical spring is relevant with rotating speed.In the case, helical spring or its some circles can directly be supported on and cover on the helical spring wall.
But also can each sliding seat or supporting base be set by seeing on helical spring length, they are support helix spring diametrically from its length opsition dependent ground.Can be about this helical spring configuration and layout or guiding with reference to DE 19912970A1, DE 19909044A1, DE 19603248A1, DE 19648342A1, DE 10209838A1 and DE 10241879A1.
What meet the requirements especially is, helical spring at least it have one with the coefficient end of lever piece in the middle of pad, these centre some corresponding profiles of pad formation, the profile acting in conjunction of these corresponding profiles and lever piece.
Advantageously, lever piece can be swung in this wise, so that mobile on a tracks when its obstruction profile between shaking peroid, and the spin axis of the relative vibration damping equipment of this tracks has a distance variation, that preferably reduce.In the case, lever piece can be swung or flexibly distortion in this wise, promptly when lever piece swing or distortion because by the loading of helical spring at circumferencial direction, the support profiles of lever piece moves in this wise along a tracks, so that the distance of the spin axis of it and torsional vibration damper reduces, and corresponding spring end is extruded on the spin axis direction or is drawn.Guaranteed thus: helical spring respective end portions supporting surface or supporting walls relatively radially pulled back and avoided frictional damping thus.
The moulding section that the profile of lever piece can pass through extension convex in a circumferential direction at least constitutes.The corresponding profile that is arranged on the corresponding spring end can be made of a groove that is located at the middle pad of this spring end, and middle pad for example is configured to load shoe.But also can conform with the destination, lever piece has a corresponding groove or a corresponding otch and this centre spacer extension moulding section is in a circumferential direction arranged.
Description of drawings
To explain other favourable structural configuration characteristic and the feature on the function following in to the description of accompanying drawing.
Accompanying drawing is represented:
The sectional drawing of a vibration damping equipment of Fig. 1,
Fig. 2 is according to the sectional drawing of Fig. 1 center line II-II, and wherein some parts does not show, so that can show the spring part that constitutes according to the present invention better,
One of Fig. 3 and Fig. 2 corresponding view, but wherein spring part or spring arm are indicated in the impaction state,
Fig. 4 modification of the present invention basically with Fig. 3 corresponding view,
Fig. 5 is according to another modification of the present invention,
Fig. 6 to Fig. 9 is used for the particularly advantageous configuration of helical spring loading cap or load shoe, and
Figure 10 to Figure 12 is used for another configuration that meets the requirements of helical spring loading cap or load shoe.
Embodiment
Vibration damping equipment 1 shown in Fig. 1 to 3 comprises a torsional vibration damper 2, and in an illustrated embodiment, this torsional vibration damper is arranged between two flywheel parts 3,4.These two flywheel parts 3,4 can reverse location with one heart, ground toward each other by bearing device 5.Flywheel part 3 for example can be connected with the output shaft of an internal-combustion engine, and flywheel part 4 then can be coupled with a transmission input shaft, for example is coupled by a friction clutcch that is assemblied on the flywheel part 4.
About the connection possibility of main structure, each flywheel part and the internal-combustion engine and the transmission input shaft of the structure of bearing means, each flywheel part and working principle thereof can be clearly with reference to DE-OS 3909892, DE-OS 4117571, DE-OS 4117579 and the prior art wherein quoted, thus, with regard to these problem aspects, the application does not need to be elaborated, therefore, the relevant therewith disclosure of prior art is regarded as combination in the present invention.
In an illustrated embodiment, torsional vibration damper 2 comprises two energy storage devices 6 that constitute by helical spring, and they are configured to integral body here.Energy storage device 6 can only be made of a spring 6a or be made up of at least one outer spring 6a and inner spring 6b that at least one is contained in this outer spring as shown in Fig. 2 and Fig. 3.Also can replace and use whole in a circumferential direction microscler helical spring 6a, 6b, and use the interconnective spring part in a plurality of front and back, for example by being advised among DE-OS 4128868 and the DE-OS 4301311 to constitute energy storage device.
When using some long helical spring 6a, 6b, just prebuckling before these helical springs can assemble according to they being arranged in vibration damping equipment 1.As appreciable from Fig. 1, these energy storage devices 6 are received in the space 7 annular or toroid, and available favourable mode is injected a kind of medium of viscosity at least in part in this space, as grease.This space 7 mainly is made of two housing parts 8,9, in an illustrated embodiment, they constitute by the plate drip molding and at least relatively helical spring 6a be configured to shelly.In an illustrated embodiment, these housing parts 8,9 connect hermetically by a soldered 10 that extends on the whole circumference.
See that in a circumferential direction space 7 annular or toroid is divided into each receiving part, holds energy storage device 6 therein.On circumference, see, each receiving part constitutes by loading zone 11,12 apart from each other, in an illustrated embodiment, these load the zone and are arranged on moulding section in the housing parts 8,9 that is configured to the plate drip molding, constitute as the press portion of groove shape by some.The loading zone 13 that is used for energy storage device 6 that is connected with second flywheel part 4 is by parts 14 carrying plate-like or annular, and these parts connect 15 in inner radial by some rivets at this and are connected with second flywheel part 4.Loading zone 13 constitutes by cantilever radially or the arm that some are molded on the external frame of parts 14 of plate-like.These arms 13 are between the loading zone 11,12 of the positioned opposite in the axial direction that is arranged on first flywheel part 3 under the situation that vibration damping equipment 1 is not loaded in the axial direction.
When pushing away between these two flywheel parts 3,4 or drawing when reversing relatively on the direction, these energy storage devices 6 and their coefficient loading zones 11,12,13 between behind a definite windup-degree that rises by position of rest shown in Fig. 2 of torsional vibration damper 2 or neutral position, be compressed at least.At least one energy storage device 6 is loaded or is supported by these arms 13 on one end thereof in traction working condition, and wherein another end of this energy storage device 6 is applied in load by loading zone 11,12.Traction working condition means: motor provides driving torque to Motor Vehicle, i.e. the engine-driving Motor Vehicle.
The end 16 of at least one energy storage device 6 does not at first load by an arm 13 in promoting operating mode, because be provided with an additional elasticity between some corresponding supporting zones 18 of the respective end portions 16 of energy storage device 6 and arm 13, this elasticity is applied by a spring part 19.The spring action of this spring part 19 is connected with the spring action of affiliated energy storage device 6.
Be provided with some support shell 17 in the space 7 of annular, as finding out from Fig. 2 and Fig. 3, these support shell surpass the length of energy storage device 6 at least and extend.These support shell are preferably coordinated with the profile phase of the circle of external spiral spring 6a and as abrasion protection.For this reason, the steel crossed by spring steel or cure process of these supporting shells 17 is made.
From the circumference of this device, these energy storage devices 6 and arm 13 preferably are similar to rotation at least and arrange symmetrically.Be provided with two energy storage devices 6 in an illustrated embodiment, they can extend on half of circumference of vibration damping equipment 1 approx.The parts 14 of described plate-like have two arms 13 on end opposite on the diameter.
In Fig. 2 and embodiment shown in Figure 3, spring part 19 constitutes one with parts 14 flange-like or plate-like.In the parts 14 of plate-like, be provided with the otch 20 of a slot shape for this reason, constitute the spring part 19 of an arm shape thus.In the case, the length of the arm 21 of Gou Chenging is determined or sizing in this wise with respect to the cross-sectional distribution of seeing on the length of arm 21 like this, and promptly such arm 21 is configured a spring that plays the bending deflection beam effect.As described in just now, connect with the spring action of energy storage device 6 by the spring action that such arm 21 produces.By the corresponding configuration of slot 20, in the support of the free end 22 of an arm 21 and an arm 13 or load the distance 23 that constitutes between the zone 18 on the definite circumference.Can determine the effective spring travel of arm 21 by this distance 23 correspondingly being determined size.In an illustrated embodiment, crossing distance 23 backs owing to the torque that acts on the corresponding flexible arm 21, this flexible arm 21 directly is supported on the arm region 13a of arm 13.In the case, slot 20 constitutes in this wise at radially outer, promptly preferably in the support of the zone 22 of the radially outer of arm 21 and corresponding arm 13 or load the support of a face of generation of part at least between the zone 18.The end 20a of a sealing of slot 20 and the transition region 21a of arm 21 are constituted in this wise, so that their pressure of occurring at the resiliently deformable owing to corresponding arm 21 can guarantee the fatigue strength of parts 14.
What conform with purpose is that slot 20 can constitute in this wise, promptly because the permission of the resiliently deformable of arm 22 has the order of magnitude windup-degree 23 2 ° and 8 ° between between---being made of two flywheel parts 3 and 4---at the parts that can reverse relatively each other here.
When rubber-like arm 21 correspondingly loaded by affiliated energy storage device 6, this arm is skew back in a circumferential direction, preferably supported or loaded on the zone 18 by putting with the zone 22 of its radially outer up to this arm 21.
As being known by Fig. 2 and Fig. 3, arm 21 has a moulding section 24 on the zone 22 of its radially outer, this moulding section 24 is equipped with under the situation of a cap shape spring seat 25 correspondingly corresponding end 16 acting in conjunction in this wise with an energy storage device 6 in the centre in the embodiment shown, so that this end regions 16 can be radially supported against the centrifugal force that acts on above it.
In an illustrated embodiment, this moulding section 24 constitutes by extension pin or projection 24 in a circumferential direction, and it can be coupled in the depression or groove 26 of circumferencial direction of a cap shape spring seat 25.Corresponding projection 24 and corresponding groove 26 are constructed in this wise each other and are arranged, promptly at least when corresponding arm 21 resiliently deformables the zone 27 of energy storage device 6 relative radially outers stopped in other words and being lifted, the circle of helical spring 6a is supported on the zone 27 of these outsides under centrifugal action.By Fig. 3 can know lift accordingly the distance 28.
More appreciable as by Fig. 2 and Fig. 3, flexible arm 21 is in the impaction state in Fig. 3 and is supported in a circumferential direction on the profile 18 of arm 13.The corresponding configuration of radially pulling back by arm 21 of the end 16 of spring 6a guarantees.Its distortion is carried out in this wise, promptly because the swing of the arm 21 that takes place or bending make corresponding protruding 24 on spin axis 29 directions of system radial displacement to take place.
As mainly being seen by Fig. 2, the zone of the inner radial of projection 24 constitutes the inclined-plane 30 of a similar acclivity, support region 31 actings in conjunction of this inclined-plane and cap shape spring seat 25.Guaranteed that by this inclined-plane 30 and with its coefficient corresponding profile 31 projection 24 is inserted in the groove 26 without a doubt.
The profile of groove 26 projection 24 and affiliated can be constructed each other in this wise, and promptly corresponding spring end 16 can produce certain displacement radially when projection 24 is inserted in the groove 26.But conform with purpose also can be, above-mentioned these profiles and corresponding profile are coordinated each other in this wise, promptly in fact projection 24 at first can be inserted in the corresponding groove 26 fully, and corresponding spring end 16 is radially inwardly drawn.Guarantee only the pulling back radially of corresponding spring end 16 thus because the distortion of this arm 21 that the loading by affiliated spring arm 21 causes produces.
Above-mentioned the pulling back and have its advantage radially of spring end 16, promptly when high rotational speed at least these end regions pulled back, some circles that this means external spiral spring 6a energy storage device or here externally do not keep in touch with other parts or zone, so that the springing freely of these spring rings, this also means and does not in fact produce frictional damping.
In addition can by arm 21 or projection 24 be used for guarantee: even in certain speed range, but the friction that exists usually between the circle of helical spring 6a and its supporting surface 27 radially outside in these speed range is big to making no longer springing of end rings, and helical spring 6a end regions still has elasticity or elastic force at least.This is particularly advantageous, so that the vibration that makes the high frequency with small angle amplitude that occurs in these speed range is by vibration damping.
As knowing from Fig. 2 and Fig. 3, the internal spiral spring 6b that the footpath upwards is arranged on external spiral spring 6a inside also is loaded by at least one cap shape spring seat 25.For this reason, corresponding cap shape spring seat 25 has one and extends to the extension of going in the end regions of corresponding spring 6a 32 in a circumferential direction, and this extension has also formed the border of groove 26.
In an illustrated embodiment, corresponding cap shape spring seat 25 is constructed in this wise, be its extension 32 in its end portion supports of correspondence of 33, one spring 6a of flange radially that has an annular on the end in the zone 22 of the outside of arm 21 on this flange.
As knowing by Fig. 3, the outside relatively support of outer spring 6a or some circles that guide surface 27 is lifted under centrifugal action radially upper support on the extension 32 of corresponding cap shape spring seat 25, the certain friction of formation between these spring rings and this extension 32 thus.But by the frictional damping that forms thus being kept less than be supported on the frictional damping that may form on the face 27 by these circles to the corresponding selection of the material that constitutes axial extension 32 and/or by corresponding coating.
As mentioned above, can be used for such spring end in an advantageous manner by the radial displacement of the arm that can swing, i.e. the spring end that in promoting operating mode, loads by flange plate 14 according to of the present invention, spring end.But also can be used for such spring end according to of the present invention, spring end by travelling backwards radially flexible or movably arm, i.e. the spring end that in traction working condition, loads by flange plate 14.What meet the requirements in addition is that two spring ends of a spring 6a can radially inwardly drawn by the arm 21 that can swing in the radial direction.
In the configuration according to Fig. 2 and Fig. 3, arm 21 has a moulding section 24 towards circumferencial direction, and it extends in the groove 26 of a cap shape spring seat 25.But conform with purpose also can be, make cap shape spring seat 25 have moulding in a circumferential direction, for this purpose and corresponding moulding section at ground structure, this moulding section is coupled in the groove in the zone of an arm 21, with the displacement radially that guarantees that corresponding spring end is desired.
A corresponding resilient arm 21 can advantageously be constructed on its shape and spring performance in this wise, and promptly it can not rest on the face 27 under centrifugal action.This by putting in order to prevent, what also meet the requirements is, is provided with some additional devices, and they can prevent this support.This for example can realize by a backstop, and this backstop and flange plate are permanently connected and stop the unallowed radially outer resiliently deformable of corresponding arm 21.
Though in an illustrated embodiment, shown lever arm 21 is configured to one with constituting the flange plate 14 that loads zone 13, and this resilient arm 21 also can constitute by additional parts.This available and following similar mode realizes: for example in DE 4433467, especially combine the described mode of Fig. 1 to Fig. 4, perhaps in DE 10119878 especially in conjunction with the described mode of Fig. 1 to Fig. 5.
In form of implementation shown in Figure 4, the lever 121 that can swing passes through at least one independently parts formation, and these parts can swingingly be supported around a rotation axis 121a.In an illustrated embodiment, lever 121 is supported on the parts 114 of flange-like swingably.Lever arm 121 can be resisted an energy storage device---swings by helical spring 134 symbol ground expression effects one by one here.Working state shown in Fig. 4 is corresponding to the working state shown in Fig. 3.
Also can use at least one butterfly spring or leaf spring to replace helical spring 134.In the case.A leg of this spring for example can hang in the corresponding hole of flange plate 114 to antitorque commentaries on classics, and another leg acts on a torsional resistance on the contrary to lever 121.For fear of the unallowed big swing of the radially outward of lever 121, as mentioned above, a corresponding backstop can be set, for example be arranged on the flange plate 114.Such backstop for example can constitute with flange plate 114 structure all-in-one-piece projectioies by one, and this projection has an axial zone, and lever 121 is supported on this axial zone.Lever 121 also can have the bump of an axial projection, and this bump is coupled in the groove of swing of a necessity relative configurations, that guarantee arm 121.Such projection or groove for example can be arranged on lever 121 and flange plate 114 axially in the overlapping areas.
Making lever arm 21 or 121 be tending towards swinging required power also can influence by the corresponding qualitative design of this lever part.
Configuration can disengageably or regularly be connected for the cap shape spring seat 25 of an end of energy storage device 6 so that particularly advantageous mode is anti-with the respective end portions of this energy storage device.This for example can realize that this connection can constitute clamping and connect by the sealed connection of shape.In this respect for example can be with reference to DE 19603248A1.As long as this connection can be arranged between corresponding cap shape spring seat and the external spiral spring 6a and/or be arranged on this cap shape spring seat and this internal spiral spring 6b between---be provided with internal spiral spring 6b.
According to a further configuration of the present invention, as representing after projection 224 is inserted in the corresponding cap shape spring seat 225, will have certain locking effect or the sealed connection of shape with the ratio of amplifying among Fig. 5.In an illustrated embodiment, this connection guarantees by locking attachment portion 236.For this reason, projection 224 acclivity 233 and cap shape spring seat 225 should have step ground to construct mutually with the coefficient corresponding profile 231 of this acclivity, so that the profile that constitutes hooks diametrically from circumferencial direction like this, and it is sealed to form certain shape thus.Can influence the power that is used for the required circumferencial direction of this connection of release by the corresponding configuration that is present in the transition region between the step.
Also allow to load corresponding energy storage device or constitute the helical spring 206a of this energy storage device at the respective end portions of the arm 221 that can swing and energy storage device 206 or this locking that on power, limits between the cap shape spring seat 225 with pulling force.As mentioned above, can be by the power join dependency between this lock portion 236 torque transmitted and, corresponding part 236 that guarantee or zone 221,225 and the 206a by this lock portion.
Owing to act at least the centrifugal force on the energy storage device of being made up of a helical compression spring 206a, being used to make this locking to connect 236, to remove required power also be this centrifugal force, so relevant with rotating speed.
Also have its advantage in the form of implementation shown in Fig. 2 to Fig. 5, promptly during the drawing in radially of energy storage device end 16, between cap shape spring seat 25 and lever arm 21 or projection 24, relative movement does not take place, can avoid relevant therewith wearing and tearing thus.
Configuration according to the present invention also allows, quality by lever 21,121,221 or mass distribution suitable be adjusted between corresponding lever and the affiliated energy storage device end and set up the moment relevant with rotating speed, this moment must be overcome by the peripheral force that is occurred between the energy storage device compression period.Also can be used as the torsional torque that applies or engine torque and under rotating speed functions control energy storage device end 16 lift the variable in distance curve.
Cap shape spring seat 325 shown in Fig. 6 to Fig. 9 is substantially with the difference of described cap shape spring seat so far: the open spaces or the groove 326 that are used to receive support protrusion 324 radially are radial outward to open on the segment section that its circumferencial direction extends at least.As especially appreciable from Fig. 6 and Fig. 7, open spaces or groove 326 are configured to the slot shape or the passage shape and are radial outward to open on the whole circumference direction is extended in an illustrated embodiment.But also can consider such embodiment, wherein set out that this open spaces 326 only extends on the part area of the extension 332 that is coupled in the spring end by end flange 333.Also can be, as long as the circumferential extension of extension 332 distance is greater than the corresponding extended distance that is coupled to the projection 324 in this extension, the end regions of the away from flange 333 of extension 332 or open spaces 326 is closed, can guarantee the more stable configuration of cap shape spring seat 325 thus.
Can see by Fig. 8 and Fig. 9, projection 324 and cap shape spring seat 325 correspondingly constitute inclined-plane coordinated with each other or inclined surface 331,331a with open spaces 326 section 325a adjacent, inner radial, they are acting in conjunction in this wise, so that corresponding spring end 316 is radially inwardly drawn when by the flange plate 314 that carries projection 324 corresponding spring 306a being compressed, and the described mode of Fig. 1 to Fig. 5 is similar with combining.Also guaranteed the springing freely of corresponding spring end 316 thus.
In Fig. 8 and form of implementation shown in Figure 9, projection 324 is configured on the flange plate 314 rigidly.But this projection also can be molded on the flexible arm that maybe can swing 21,121,221 similarly with combining the described mode of Fig. 1 to Fig. 5, and this arm is by the component load-bearing of a flange plate or plate-like.
The opening wide at least in part of groove or open spaces 326 makes the projection 324 can free configuration, because at least in the section adjacent of extension 332 with flange 333, projection 324 can constructed widelyer in the radial direction, and can have higher resistance to flexure at least in this zone thus.Therefore the additional position radially of projection 324 can be obtained being used for by the respective configuration of a cap shape spring seat 325, under the situation that intensity equates at least, longer projection 324 can be obtained thus.But on material thickness, be configured to thicker with projection 324 supporting zone 325a coefficient, inner radial according to what the configuration of cap shape spring seat 325 of the present invention also allowed cap shape spring seat 325, can make the improved strength of cap shape spring seat opposing centrifugal force thus, this centrifugal force is acted on this cap shape spring seat by spring 306a.
Pass through the possibility of the more long support projection of use 324 that realized, also can use some to have the cap shape spring seat 325 of longer extension 332.Can guarantee to support diametrically the spring ring of greater number thus.As appreciable, in the state of the unloading of spring 306a, can support at least 5 spring end circles by cap shape spring seat 325 from Fig. 8.
By also making cap shape spring seat 325 and the corresponding adaptive or configuration coefficient support profiles radially of spring 306a on the degree that the stress that forms in the circle of the end regions of spring 306a is limited in allowing.Therefore the circle of the corresponding moulding of the support profiles by cap shape spring seat 325 or the formation end regions that configuration also can be determined spring 306a radially bends variation under centrifugal action.
As especially as seen from Figure 9, the spring-loaded zone 324a that is positioned at protruding 324 inner radial of flange plate 314 and be positioned at spring-loaded zone 324b setting each other on the circumferencial direction of vibration damping equipment 301 of protruding 324 radially outers with staggering.In an illustrated embodiment, this dislocation between spring-loaded zone 324a and 324b is by such sizing, promptly they in fact side by side rest on the flange 333 of cap shape spring seat 325 on the one hand, and rest on the other hand on the end rings 316a of spring 316.
But can favourablely be that flange 333 is interrupted or returns wrong in the zone of the spring-loaded zone of the inner radial of flange plate 314 324a in a circumferential direction, and is such, guarantees thus that promptly end rings 316a directly is supported on the regional 324a of flange plate.In this configuration, the spring-loaded of flange plate 314 zone 324a and 324b look up and can be aligned from the footpath.
Supporting part 425 shown in Figure 10 to Figure 12 has realized that also the end rings of spring end 416 radially supports to be similar in conjunction with cap shape spring seat 325 described modes.As appreciable by Figure 12, face 431a as inclined-plane and inclined surface face 431 that work, flange plate projection 424 and supporting part 425 in this illustrated embodiment coordinates each other in this wise, promptly during flange plate projection 424 is inserted into insertion stage in the supporting part 425 of the cross section that is configured to U-shaped, between these two faces 431 and 431a, has face all the time and contact.Can reduce occurring wear on these faces significantly thus.In an illustrated embodiment, these faces 431 and 431a are configured to the spin axis of vibration damping equipment arc and relative and correspondingly arrange, so that guarantee this face contact.
Meet the requirements though supporting part 425 is made of high-intensity plastics, shown form of implementation is suitable for by the light sheet material manufacturing.In order to guarantee corresponding sliding properties, the sliding properties in the zone of face 431a especially, this sheet material or supporting part 425 are provided with the glide material bed of material at least on face 431a.In addition, what especially meet the requirements is that this supporting part 425 is hardened in the zone of face 431a at least.These parts 425 are made by sheet material (sheet metal) has its advantage, and promptly these parts need not cutting by simple shaping processing and promptly can be made into.This has just realized the cheap manufacturing of this supporting part cost.
As mentioned above, this supporting part 425 is configured to the cross section of U-shaped and has two contact pin or tongue piece 434,435, and they are in lateral projections.These tongue pieces 434,435 are supported on the end rings 436 of corresponding spring, as seen from Figure 12.Zone 434,435 is used for simultaneously spring end zone 416 being loaded.
Because the material load that inner stress causes, these internal stresss are by the support radially of corresponding spring end 416 and are carried in the parts 425 and occur that this supporting part 425 has corresponding free otch 437 in order to reduce.
As finding out in conjunction with Figure 10 and 11, supporting part 425 has moulding part 438, they here constitute by the zone 438 of some tab shaped, these zones relatively other zone of supporting parts 425 are out of shape in this wise, so that they extend in the open spaces 426 that the configuration of the U-shaped by supporting part 425 forms.In the case, these zones 438 constitute some supporting surfaces, and having of flange plate 414 obverse protruding 424 rests on these supporting surfaces, and this corresponding surface for example constitutes by stage.
As especially also appreciable by Figure 11 and Figure 12, supporting part 425 has a moulding part 439, and this moulding part constitutes a projection 439 of radially inwardly pointing to here.As appreciable by Figure 12, this moulding part 439 is stuck between two circles of spring end 416, has guaranteed anti-detachment between corresponding spring end 416 and affiliated supporting part 425 thus.
These embodiments should not be counted as limitation of the present invention.And in scope disclosed by the invention, can have numerous variations and modification, especially some modification, parts and combination and/or material, they for example by each with described in general remark, form of implementation and the claim and accompanying drawing in the feature that comprises or parts or method step combine and can know by inference in view of its task of solution for the professional workforce, or draw a new technological scheme or new method step or method step order, and be with regard to they relate to manufacturing, check and method of work by feature capable of being combined.
The drawing reference numeral inventory
1 vibration absorber
2 torsional vibration dampers
3,4 flywheel parts
5 supporting arrangements
6 energy storage devices
6a, 6b helical spring
The space of 7 toroid
8,9 housing parts
10 soldereds
11,12,13,13a loads the zone
The parts of 14 plate-likes
15 rivets connect
16 ends
17 support shell
18 supporting zones
19,19a spring part
20,20a slot
21,21a arm
22 free ends
23 windup-degrees
24 moulding sections
25 cap shape spring seats
26 grooves
27 zones
28 lift distance
29 spin axiss
30 inclined-planes
31 support regions
32 extensions
33 cantilevers
114 parts
121 levers
The 121a rotation axis
134 helical springs
135 zones
206 energy storage devices
The 206a helical compression spring
221 arms that can swing
224 projectioies
225 cap shape spring seats
231 corresponding profiles
233 acclivities
236 locking attachment portions
The 306a spring
314 flange plate
316,316a spring end
324 support protrusion
324a, 324b load the zone
325 cap shape spring seats
The 325a section
326 grooves
331,331a inclined surface
332 extensions
333 end flange
414 flange plate
416 spring ends
424 flange plate projectioies
425 supporting parts
431,431a face
434,435 contact pin or tongue piece
436 end rings
437 free otch
438,439 moulding parts
Claims (12)
1. the torsional vibration damper that has an input block and an output block, input block and output block can be resisted the effect of some energy storage devices that work and reverse each other between them, wherein these energy storage devices have the compressible helical spring at least one circumferencial direction that is arranged on vibration damper basically, in addition, by one in these parts at least one lever piece that can swing in a circumferential direction of carrying, wherein at least between input block and output block during relative reversing, helical spring can be supported on in the end of its circumferencial direction on this lever piece in this wise, so that make this lever piece carry its parts swing relatively owing to reverse relatively, it is characterized in that: this lever piece has some profiles, these profiles be arranged on helical spring corresponding end on the such acting in conjunction of corresponding profile, so that between the shaking peroid of the circumferencial direction of this lever piece, helical spring at least one end section is stopped diametrically against the centrifugal force ground that acts on this spring section.
2. according to the torsional vibration damper of claim 1, it is characterized in that: lever piece constitutes by the spring part that is configured to bending deflection beam form.
3. according to the torsional vibration damper of claim 1, it is characterized in that: lever piece be supported on input block and/or the output block swingably and the effect that can resist an additional energy storage device around its supporting swing.
4. according to one torsional vibration damper in the claim 1 to 3, it is characterized in that: input block or output block are made of the parts of flange plate form, and these parts are carrying at least one lever piece.
5. according to one torsional vibration damper in the claim 1 to 4, it is characterized in that: but the lever piece of antagonistic spring effect swing and helical spring are connected between input block and the output block using.
6. according to one torsional vibration damper in the claim 1 to 5, it is characterized in that: helical spring extends on the circumferencial direction of torsional vibration damper and produces a friction relevant with centrifugal force, in parallel with helical spring spring action in that torsional vibration damper is inner, and is relevant with rotating speed by the dynamic torsional resistance that helical spring always produces thus.
7. according to one torsional vibration damper in the claim 1 to 6, it is characterized in that: output block or input block have one and cover helical spring wall in the axial direction, helical spring or directly by its some circles or indirectly by the supporting part in the middle of placing at least in the centrifugal action lower support on this wall.
8. according to one torsional vibration damper in the claim 1 to 7, it is characterized in that: pad helical spring carries at least on itself and coefficient end of lever piece in the middle of, this centre pad constitutes some corresponding profiles, the profile acting in conjunction of these corresponding profiles and lever piece.
9. according to one torsional vibration damper in the claim 1 to 8, it is characterized in that: lever piece can be swung in this wise, so that move on a tracks at its obstruction profile between shaking peroid, the spin axis of the relative vibration damping equipment of this tracks has the distance of a variation.
10. according to one torsional vibration damper in the claim 1 to 9, it is characterized in that: lever piece can be swung in this wise, promptly when lever piece is swung because by the loading of helical spring at circumferencial direction, these support profiles of lever piece move in this wise along a tracks, so that it reduces with the distance of the spin axis of torsional vibration damper, and corresponding thus spring end quilt is pushed towards the spin axis direction.
11. according to one torsional vibration damper in the claim 1 to 10, it is characterized in that: these profiles of lever piece constitute by the moulding section of extension convex in a circumferential direction at least.
12., it is characterized in that according to one torsional vibration damper in the claim 1 to 11: be arranged on the corresponding spring end corresponding profile by one be arranged on the corresponding spring end in the middle of the groove of pad constitute.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102004037416.3 | 2004-07-30 | ||
| DE102004037416 | 2004-07-30 | ||
| DE102004045113.3 | 2004-09-17 | ||
| DE102004059457.0 | 2004-12-10 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1727723A true CN1727723A (en) | 2006-02-01 |
| CN100449168C CN100449168C (en) | 2009-01-07 |
Family
ID=35927161
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005100910811A Expired - Fee Related CN100449168C (en) | 2004-07-30 | 2005-08-01 | Torsional vibration damper |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100449168C (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102171485A (en) * | 2009-03-13 | 2011-08-31 | 爱信精机株式会社 | Damper device |
| CN101663502B (en) * | 2007-05-14 | 2012-07-11 | 博格华纳公司 | Shoe having a spring position limitation, or torsional oscillation damper having such a shoe |
| CN102132066B (en) * | 2008-09-23 | 2013-05-29 | Valeo离合器公司 | Dual damper flywheel, in particular for an automobile |
| CN102124247B (en) * | 2008-08-27 | 2013-08-07 | 株式会社艾科赛迪 | Flywheel assembly |
| CN103998806A (en) * | 2011-12-22 | 2014-08-20 | 丰田自动车株式会社 | Torsional vibration dampening device |
| CN105090435A (en) * | 2014-04-15 | 2015-11-25 | 福特全球技术公司 | Vehicle flexible drive plate with torsion damper |
| CN105443603A (en) * | 2015-12-18 | 2016-03-30 | 陕西航天动力高科技股份有限公司 | Wet lockup clutch for hydraulic torque converters |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB511798A (en) * | 1938-02-25 | 1939-08-24 | Noel Banner Newton | Improvements in or relating to clutch plates |
| FR2676789A1 (en) * | 1991-05-23 | 1992-11-27 | Valeo | TORSION SHOCK ABSORBER, ESPECIALLY FOR MOTOR VEHICLES. |
| FR2698933B1 (en) * | 1992-12-09 | 1995-03-10 | Valeo | Torsional damper, especially for a motor vehicle. |
| DE4433467C2 (en) * | 1993-09-28 | 2003-04-17 | Luk Lamellen & Kupplungsbau | torsional vibration damper |
| DE10119878B4 (en) * | 2000-05-17 | 2013-02-07 | Schaeffler Technologies AG & Co. KG | Torsionsschwingunsdämpfer |
-
2005
- 2005-08-01 CN CNB2005100910811A patent/CN100449168C/en not_active Expired - Fee Related
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101663502B (en) * | 2007-05-14 | 2012-07-11 | 博格华纳公司 | Shoe having a spring position limitation, or torsional oscillation damper having such a shoe |
| CN102124247B (en) * | 2008-08-27 | 2013-08-07 | 株式会社艾科赛迪 | Flywheel assembly |
| CN102132066B (en) * | 2008-09-23 | 2013-05-29 | Valeo离合器公司 | Dual damper flywheel, in particular for an automobile |
| CN102171485A (en) * | 2009-03-13 | 2011-08-31 | 爱信精机株式会社 | Damper device |
| US8968150B2 (en) | 2009-03-13 | 2015-03-03 | Aisin Seiki Kabushiki Kaisha | Damper device |
| CN102171485B (en) * | 2009-03-13 | 2015-04-15 | 爱信精机株式会社 | Damper device |
| CN103998806A (en) * | 2011-12-22 | 2014-08-20 | 丰田自动车株式会社 | Torsional vibration dampening device |
| CN105090435A (en) * | 2014-04-15 | 2015-11-25 | 福特全球技术公司 | Vehicle flexible drive plate with torsion damper |
| CN105443603A (en) * | 2015-12-18 | 2016-03-30 | 陕西航天动力高科技股份有限公司 | Wet lockup clutch for hydraulic torque converters |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100449168C (en) | 2009-01-07 |
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Owner name: LUK VERMOEGENSVERWALTUNGSGESELLSCHAFT MBH Free format text: FORMER OWNER: LUK LAMELLEN UND KUPPLUNGSBAU GMBH Effective date: 20130529 Owner name: SCHAEFFLER TECHNOLOGY GMBH + CO. KG Free format text: FORMER OWNER: LUK VERMOEGENSVERWALTUNGSGESELLSCHAFT MBH Effective date: 20130529 |
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Effective date of registration: 20130529 Address after: German Boer Patentee after: Luke Asset Management Co.,Ltd. Address before: German Boer Patentee before: LUK LAMELLEN UND KUPPLUNGSBAU BETEILIGUNGS KG Effective date of registration: 20130529 Address after: German Herzogenaurach Patentee after: SCHAEFFLER TECHNOLOGIES AG & CO.KG Address before: German Boer Patentee before: Luke Asset Management Co.,Ltd. |
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Granted publication date: 20090107 Termination date: 20180801 |