CN107002816B - The transmission system of torsional vibration damper and the motor vehicles for having the torsional vibration damper - Google Patents
The transmission system of torsional vibration damper and the motor vehicles for having the torsional vibration damper Download PDFInfo
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- CN107002816B CN107002816B CN201580059844.6A CN201580059844A CN107002816B CN 107002816 B CN107002816 B CN 107002816B CN 201580059844 A CN201580059844 A CN 201580059844A CN 107002816 B CN107002816 B CN 107002816B
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- vibration damper
- torsional vibration
- substrate
- lever
- lever element
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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
- F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
- F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
- F16F15/1464—Masses connected to driveline by a kinematic mechanism or gear system
- F16F15/1471—Masses connected to driveline by a kinematic mechanism or gear system with a kinematic mechanism, i.e. linkages, levers
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- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The present invention relates to a kind of torsional vibration damper (2), including can be around the substrate (18) that rotation axis (16) rotate and can be relative to substrate (18) and the inertia mass part (20) rotated against the reset force of resetting apparatus (36), wherein resetting apparatus (36) has for generating the spring unit (38) that power is arranged.The pivotable lever element (40) that there is resetting apparatus (36) at least one can pivot around pivotal point (46), the reset force of inertia mass part (20) is influenced via the reset force junction (44) of lever element (40) by generating, via the lever element (40), power, which is arranged, from the setting power junction (42) of lever element (40) can be transferred to inertia mass part (20).The invention further relates to a kind of transmission systems (110) for the motor vehicles with such torsional vibration damper (2).
Description
The present invention relates to a kind of torsional vibration damper, including can be around the substrate that rotation axis rotates and can be relative to
Substrate and the inertia mass part rotated against the reset force of resetting apparatus, wherein resetting apparatus has for generating setting power
Spring unit.The invention further relates to a kind of transmission systems for the motor vehicles with such torsional vibration damper.
199 07 216 C1 of DE discloses a kind of torsional vibration damper, is that can revolve around rotation axis with form
The base component of the support plate turned.Coasting body is arranged on the supporting plate, can be relative to base component answering against resetting apparatus
Position power rotation.Resetting apparatus has flexure spring, which radially extends, and is on the one hand arranged on base component, another party
Face is arranged in inertia member.If coasting body is rotated relative to base component, flexure spring is for having a direct impact
The setting power of coasting body, thus setting power similarly indicates to influence the reset force of coasting body.Coasting body is radially supported at branch
It is the side occurred in support plate radially on fagging, wherein cartridge housing is arranged on the supporting plate thus, and coasting body is along diameter
To being supported on cartridge housing, and along the circumferential direction guide.Existing torsional vibration damper has disadvantage, because resetting apparatus needs
Larger and intensive installation space flexure spring, especially when resetting apparatus on the one hand be necessarily placed on coasting body, another party
When face is arranged on the supporting plate.As previously mentioned, on the one hand on the other hand setting is arranged on coasting body on the supporting plate for support
The necessity of flexure spring also causes setting of the flexure spring on whirling vibration sensor to be largely predefined.
Therefore, in the torsional vibration damper of the type, the flexible setting of flexure spring is impossible.In addition, passing through support
Mounting shell on plate radially supports coasting body needs torsional vibration damper to have more complex knot on the supporting plate
Structure, wherein wear in the region of support coasting body at this external support board and also increase.
From the prior art, the present invention is major problem is that create the rotation with the structure for simplifying and saving installation space
Rotational oscillation fluctuation dampers, wherein the special flexible setting of spring unit is feasible.In addition, main problem of the invention is to create to use
In the transmission system of the motor vehicles with such advantageous torsional vibration damper.
By feature listed by claim 1 or claim 12, which is addressed.Advantageous embodiment of the invention is
The theme of dependent claims.
Torsional vibration damper according to the present invention has the substrate that can be rotated around rotation axis.For example, substrate can be by
It can substantially be formed in the substrate or support plate of radial direction extension, when necessary for biradical plate or dual-gripper plate.In addition, whirling vibration
Damper have can around rotation axis, relative to substrate and against the reset force of resetting apparatus rotation inertia mass part.It is multiple
Position device has the spring unit for generating setting power, and wherein spring unit can have, for example, one or more spring elements
Part.In addition, resetting apparatus have can be around pivotal point pivotable lever element.Therefore, pivotable lever element can, for example,
It pivots via pivotal point or is directly pivoted on substrate indirectly.Thus, it is preferred that lever element is by torsional vibration damper
The plane that determines of radial direction on [operating], and therefore can prolong around the pivotal point on torsional vibration damper axis direction
The axis stretched and pivot.In addition, pivotably lever element is preferably counter-bending or rigid lever element.Lever element setting exists
Between spring unit positioned at side and the inertia mass part positioned at the other side, in this way, the setting power that spring unit generates can
It is transmitted to inertia mass part from the setting power junction on lever element, and generates reset force, via the reset of lever element
Power junction influences inertia mass part.The advantage is that: the spring unit for generating the resetting apparatus of setting power is not required to directly affect
Inertia mass part, but in fact may be provided in another point on the substrate of torsional vibration damper, in this way,
Saving space and the setting of flexible spring unit in torsional vibration damper are feasible.On the other hand, due to lever element,
Lever ratio can be set or be specified, the reset force on inertia mass part is acted on based on lever element and is more than or less than by resetting apparatus
Spring unit generate setting power.Therefore, by not needing the especially rigid spring unit for generating setting power
In the case of specify lever ratio, the rigidity of resetting apparatus can increase in a targeted way.Therefore, it should initially record, spring list
Member is only had lower spring stiffness and therefore can be formed with a kind of special section space-efficient mounting means, wherein furthermore
The flexible setting of spring unit on the substrate of torsional vibration damper is feasible.
In the preferred embodiment of torsional vibration damper according to the present invention, lever element side is via substrate or lever
Supporting track support on element may be supported on substrate, and the other side is via can be along the branch on lever element or substrate
The rotational roller unit supports or may be supported on substrate that support track rolls.Preferably, here, substantially in radial direction
Support is achieved.Due to roller unit, in this embodiment when lever element is pivoted around pivotal point, realizes and be difficult to discover
And lesser abrasion, wherein still can guarantee that there is the lever element on substrate equivalent stablizing to support.In this embodiment, it can mention
For the supporting track being connect with roller unit, for example, in pivotal point region.Alternatively or supplementarily, the branch being connect with roller unit
Support track may be provided in the region at setting power junction, this will be described in detail later in this article.
Therefore, in a particularly preferred embodiment of torsional vibration damper according to the present invention, power junction is set
It can be moved along supporting track rotating inertial mass part by relative to substrate and.Therefore, in this embodiment, in setting power
On junction, supporting track or roller unit interact with roller unit or supporting track.It is in this way, it can be achieved that especially simple
Single structure also assures that the abrasion when above-mentioned lever element pivots between lever element and substrate is smaller.
Substantially, above-mentioned roller unit can be formed by simple wheel or simple roller, and one side is rotatably arranged but consolidates
It is scheduled on lever element or substrate, the other side can roll on the supporting track that substrate or lever change part.According to the present invention
In another preferred embodiment of torsional vibration damper, roller unit is formed by roller bearing substantially, is thereby realized above-mentioned excellent
It puts and realizes equivalent cramped construction.Therefore, roller bearing preferably have inside race, outer race and setting inside race with
Rolling element between outer race.Therefore, inside race is preferably fixed and is arranged on lever element or substrate, and when necessary
It is set as not rotating, and due to the rolling element between interior outer race, outer race can be in substrate or the supporting track of lever element
Upper rolling.Roller bearing is preferably needle bearing, to realize being loaded into and being equal to compact structure for roller unit.
In the advantageous embodiment of torsional vibration damper according to the present invention, spring unit has for generating setting power
At least one helical spring.Helical spring can be, for example, spiral compression spring and/or spiral stretching spring, are arranged in substrate
Recess portion in.
In other advantageous embodiments of torsional vibration damper according to the present invention, at least one displaceable support bottom
Plate is arranged on the helical spring in recess portion, at least provided with a helical spring on recess portion, wherein helical spring, via facing
Support baseboard in the support-side of the recess portion of helical spring is supported outward or can be supported in radial direction.Therefore, bottom is supported
Plate has the advantage that helical spring will not directly be supported or can be supported in the support-side of recess portion, to minimize spiral shell
Revolve the potential fretting wear of the support-side of spring or recess portion.By proper choice of the material for being used to support bottom plate, abrasion can also subtract
Small, wherein support baseboard is preferably made of plastics, and the support-side of helical spring and/or recess portion particularly preferably by metal or
Steel is formed.Roller unit can also act between support baseboard and the support-side of recess portion in an advantageous manner, to substantially reduce
Abrasion between support baseboard and the support-side of recess portion, other advantageous embodiments of torsional vibration damper according to the present invention are just
It is such case.Therefore, the correspondence rotational roller that can be rolled on support baseboard may be provided at such as support baseboard sheet.
Substantially, support baseboard can only prolong in the inner space of the helical spring surrounded by the winding part of helical spring
It stretches, to influence the support on recess supports side by this method.In especially having for torsional vibration damper according to the present invention
In the embodiment of benefit, support baseboard alternatively or supplementarily extends between the periphery of helical spring and the support-side of recess portion, from
And influence particularly stable support.Support bottom is placed by the middle position between helical spring periphery and the support-side of recess portion
Plate or at least one support baseboard part, helical spring can also be supported or can be supported in the support-side of recess portion.
In other preferred embodiments of torsional vibration damper according to the present invention, support baseboard is arranged in helical spring
Between periphery and recess supports side, another support bottom of the helical spring on the support baseboard of side and the substrate of the other side
The gap being located between helical spring periphery and recess supports side is generated on helical spring region between plate or supporting point.
Therefore, supporting point preferably specifies the end side supporting point for being supported on helical spring on substrate, wherein (as must) its
It can be realized by support baseboard.The advantages of embodiment is: helical spring can be by the higher rotational of torsional vibration damper
Under centrifugal force effect and be bent laterally toward its extending direction, and helical spring will not be with the support side contacts of recess portion, especially
Ground, helical spring is flexible or extends into above-mentioned gap.Therefore, gap or its size are preferably selected such that: if rotation
Vibration damper is driven in transmission system with maximum rotative speed, then is not occurred between helical spring and the support-side of recess portion
Contact.
Above-mentioned support baseboard can be substantially provided in all positions in recess portion, so that helical spring passes through support baseboard
It is supported in the support-side of recess portion.However, in other preferred embodiments of torsional vibration damper according to the present invention, support
The setting of bottom plate following manner is formed: the setting power of spring unit can be transmitted to the setting power engagement of lever via support baseboard
Point.Therefore, support baseboard is formed as, for example, being used for the end bottom plate of helical spring, the end side phase interaction with helical spring
The setting power of spring unit is transmitted to setting power junction.However, as described above, it is also contemplated that other support baseboards,
The setting power of spring unit will not be transmitted to setting power junction by these support baseboards, and be used only as helical spring being supported on
In the support-side of recess portion or above-mentioned supporting point.
In other particularly preferred embodiments of torsional vibration damper according to the present invention, support baseboard and lever member
Part is supported via roller unit and supporting track or can be supported on substrate.As described above, support baseboard and lever element warp
It is supported by roller unit and supporting track or can be supported on substrate, preferably in the region at setting power junction.One side
Face, the embodiment have the advantage that the support by roller unit and supporting track, abrasion are reduced, lead to support baseboard
On fretting wear it is smaller and guarantee support baseboard have simple mobility.On the other hand, above-mentioned Section 2 function,
The additional support of support baseboard, is assigned on current roller unit and supporting track i.e. on substrate, thus at least in the region
Additional roller unit or supporting track are not needed, which strongly simplifies the structures of torsional vibration damper.
In other advantageous embodiments of torsional vibration damper according to the present invention, there are two be located at thick stick for spring unit tool
On rod element and interact with each other helical spring.Thus, for example, it is possible to provide two spiral compression springs or two spirals are drawn
Stretch spring.However, two helical springs are all formed as spiral stretch and compressed spring is also feasible.
If there are two the helical springs for realizing setting power for spring unit tool, in whirling vibration according to the present invention
In other preferred embodiments of damper, above-mentioned support baseboard forms the support baseboard for being used for a helical spring and for another
The support baseboard of one helical spring.In this way, not only number of parts is reduced, moreover, especially when support baseboard is that will set
When setting power and being transmitted to the support baseboard at setting power junction of lever element, the appropriate phase of two helical springs of setting power is generated
Interaction is guaranteed.In this embodiment, it is further preferred that, if support baseboard is formed as an entirety, wherein such as
The upper support baseboard is preferably made of plastics.
In other advantageous embodiments of torsional vibration damper according to the present invention, the mass center setting of lever element is being set
Set position in the level at power junction or more more outside than setting power junction in radial direction.
In other preferred embodiments of torsional vibration damper according to the present invention, the mass center of lever element is in radial side
To the position more more outside than pivotal point, which particularly develops advantage (but non-exclusive) and will be described below,
Wherein reset force junction keeps its setting relative to lever element.It has the advantage that lever element, is based only upon centrifugation
Power tends to return to its starting pivot position.Therefore, advantageously: the mass center of lever element is arranged in radial direction
At the level at the reset force junction in direction, and preferably in the position more more outside than reset force junction in radial direction
On, to more amplify above-mentioned advantage.
In other advantageous embodiments of torsional vibration damper according to the present invention, when viewed from the axial direction, if
Set external position (at least in the axial direction) more than pivotal point lever element mass center setting one with pivotal point and/
Or in the common linear or common radial line at reset force junction and/or setting power junction.Therefore, the listed matter of lever element
The heart is preferably provided in pivotal point and/or reset force junction and/or is arranged the lever on the common radial line at power junction
The initial position of element or inertia mass part.In this way, centrifugal force will not be to lever member if lever element is located at its initial position
Part has an impact or influences very little.
In other preferred embodiments of torsional vibration damper according to the present invention, it is preferably thin that lever element, which has,
Elongated lever piece and lever mass part.Lever mass part is fixed on lever piece, and makes the mass center of lever element in diameter
It is more more outside than the mass center of lever piece to direction.Therefore, lever mass part is preferably inherently created with lever piece or and thick stick
Rod piece is formed separately.The formation intrinsic with lever piece of lever mass part has the advantage that manufacture is simplified, and is especially making
Lever mass part can be manufactured together during making lever piece.On the contrary, lever mass part is separated with lever piece, have the advantage that
It can be applied to the lever piece manufactured, to be positioned in a targeted way and lever mass part is applied on lever piece
The mass center of entire lever element.About the lever mass part for separating and being formed with lever piece, it is more preferred to, via fastening
It puts removably or is unreleasably fastened on lever piece.In the case it is also preferred that lever mass part can fasten
It can be positioned at least two different fastening points and/or securely along lever piece, so as to then influence lever element
Mass center.
In other particularly preferred embodiments of torsional vibration damper according to the present invention, in order to by inertia mass
Part especially fastens in radial direction and supports or be mounted on substrate with will not generating excessive friction loss, and inertia mass part is logical
It crosses at least three rollers and is supported or can be supported on substrate in radial direction.
In other preferred embodiments of torsional vibration damper according to the present invention, roller side is rotatably secured to inertia
In mass member or substrate, and the other side can roll on substrate or inertia mass part.For example, can be via inertia mass part or base
Part realizes fixation of the roller on inertia mass part or substrate, wherein when inertia mass part or substrate are relative to substrate or inertia mass
Roller is carried by roller support when part rotates, but it can be rolled on substrate or inertia mass part.It is preferred, therefore, that roller is set as
It is fixed on inertia mass part or substrate relative to circumferencial direction.
In other preferred embodiments of torsional vibration damper according to the present invention, above-mentioned roller can be in substrate or inertia matter
It is rolled on roller rail on amount part, central roll rail is set as circumferential exterior in radial directions, and radius is substrate maximum radius
80%(be when necessary 90%).In this way, it is more outside in radial direction to ensure that roller may be configured as, and it is not required to be supported
In the longer roller support in radial direction, so that the structure of torsional vibration damper is simplified, weight is subtracted
It is few.It is thus particularly advantageous to which roller rail is arranged in the maximum radius of substrate, and roller is preferably provided on inertia mass part.
On the contrary, being preferably, the roller rail being arranged on inertia mass part is arranged in radial direction if roller is arranged on substrate
Radius is greater than the maximum radius of substrate outside substrate, thus where it.
As described above, the installation via roller and inertia mass part thus on substrate, may be implemented inertia mass part
Stablize on substrate in radial direction and the support of more abrasion will not be generated.In torsional vibration damper according to the present invention
In other advantageous embodiments, inertia mass part be further supported via at least one roller along at least one axial direction or into
One step can be supported, preferably along two axial directions.Therefore, in this embodiment, difunctional, one side is specified to roller
Face generates the support in radial direction, on the other hand generates the support between inertia mass part and substrate in the axial direction, from
And structure can be further simplified, particularly, does not need further or additional in the axial direction support inertia mass part
Means on substrate.
In other advantageous embodiments of torsional vibration damper according to the present invention, it is fixed to inertia mass part or substrate
On at least one roller on the outside of be provided with peripheral groove, substrate or inertia mass part extend into the groove.The embodiment has
Following advantages: the peripheral groove in roller can be manufactured easily in the environment for generating roller, in this way, torsional vibration damper is as a whole
Generation is simplified.
In other preferred embodiments of torsional vibration damper according to the present invention, groove is arranged in substrate or inertia matter
It measures on part, roller extends into groove to generate at least one axial direction, preferably on two axial directions to inertia matter
Measure the support of part.
In other advantageous embodiments of torsional vibration damper according to the present invention, lever element has to be connect in setting power
The first lever segment between chalaza and pivotal point and the second lever segment between pivotal point and reset force junction,
Length can change and relative to substrate rotating inertial mass part, while keep lever ratio substantially.
In other advantageous embodiments of torsional vibration damper according to the present invention, by the length for changing lever segment
Degree, pivotal point and reset force junction can be mobile relative to lever element, while reset force junction keeps it relative to lever
The setting of element.It has been shown that torsional vibration damper is in centrifugal force under higher rotational and exists in embodiment deformation
Influence on lever element position is reduced, and lever element can relatively easily return to its initial position.In addition, compared to pivot
The example of turning point is preferably in this embodiment, and setting power is set as closer from rotation axis in radial directions.Also it should say
It is bright, be preferably in this embodiment, be arranged the radial distance between power junction and rotation axis be less than between pivotal point and
Radial distance between rotation axis.
In other advantageous embodiments of torsional vibration damper according to the present invention, the substitution of above-described embodiment is shown,
By changing the length of lever segment, pivotal point and reset force junction can be mobile relative to lever element, while reset force connects
Chalaza keeps its setting relative to lever element.The embodiment is advantageous, when especially in conjunction with above-described embodiment, according to this
Embodiment, the mass center of lever element are set as more more outside than pivotal point in radial directions, are preferably at least in radial direction
In the level at upper reset force junction, it is therefore particularly preferred that it is more more outside than reset force junction in radial directions, thus real
Existing above-mentioned advantage.
In other preferred embodiments of torsional vibration damper according to the present invention, reset force junction can pass through change
The reset force indicatrix of reset force and adjust.Thus, for example, influencing inertia mass part by by adjusting reset force device
The gradient of reset force indicatrix of reset force can increase or decrease, so that correspondingly the rigidity increasing of reset force device adds deduct
It is few.Therefore, the reset force device neatly made a response to working condition in transmission system is generated.
In other preferred embodiments of torsional vibration damper according to the present invention, the reset of change reset force can be passed through
Power indicatrix and the lever ratio for changing lever element.In this embodiment it is preferred that the thick stick of change lever element can be passed through
Bar ratio adjusts pivotal point, and pivotal point is changeable relative to the position of substrate.Thus, for example, pivoting, may be configured as can be in substrate
Upper movement, pivot point are in radial directions preferred relative to the movement of substrate or in the movement of radial line.In addition,
In the embodiment preferably, pivotal point is formed by prominent protrusion adjustable or displaceable on substrate.
In other particularly advantageous embodiments of torsional vibration damper according to the present invention, the mass center of lever element is arranged
In pivot of the radial direction than at least one setting position of adjustable pivotal point the setting position of pivotal point (no matter or)
The more outside position of turning point, to realize that the mass center of above-mentioned lever element is more arranged in radial direction than pivotal point outward
The advantages of.
Drive train according to the present invention for motor vehicles has such torsional vibration damper according to the present invention,
Its substrate is rotatably secured on the component of transmission system.Therefore, substrate can be affixed basically to the transmission system of rotation vibration
On any component.
In the preferred embodiment of drive train according to the present invention, the substrate of torsional vibration damper is rotatably fixed to pacify
It is attached to component, which is that the input side, torque-vibration damper or double quality of torque-vibration damper or double mass flywheel fly
The outlet side of wheel, the input side of arrangement of clutch, when necessary for input side disc holder or input side disc holder radial support,
The outlet side of the outlet side of arrangement of clutch, the input side of speed changer and/or speed changer.Therefore, influence respectively above-mentioned two point it
One two or more torsional vibration dampers unquestionably can be set in transmission system.
In the particularly preferred embodiment of drive train according to the present invention, the outlet side of arrangement of clutch is outlet side disc holder
Or the radial support of outlet side disc holder, substrate are rotatably fixedly installed to the outlet side of arrangement of clutch, which increase defeated
The engine speed intensity of side panel bracket or the radial support of outlet side disc holder out.Therefore, substrate is rotatably fixed pacifies
Mounted in the radial support of outlet side disc holder or outlet side disc holder, and strengthen outlet side disc holder or output side panel
The radial support of bracket.
Later, the present invention will be described by reference to the exemplary embodiment of attached drawing in more detail.It is as follows:
Fig. 1 is the front view of the embodiment of torsional vibration damper of the initial position according to the present invention with lever piece；
Fig. 2 is the view for the torsional vibration damper that lever element pivots out initial position in Fig. 1；
Fig. 3 be in Fig. 1 and 2 torsional vibration damper along first embodiment deform in straight line A-A partial view；
Fig. 4 be in Fig. 1 and 2 torsional vibration damper along second embodiment deform in straight line A-A partial view；
Fig. 5 is the schematic of the embodiment of the transmission system of at least one torsional vibration damper with good grounds Fig. 1 to 4
It indicates.
Fig. 1 and 2 shows the embodiment of torsional vibration damper 2 according to the present invention.In the drawings, by corresponding
Arrow shows the opposite axial direction 4,6 of torsional vibration damper 2, opposite radial direction 8,10 and opposite circumferencial direction
12,14, opposite direction of rotation can also be designated as.Torsional vibration damper 2 has 4,6 rotation extended in the axial direction
Axis 16.
Torsional vibration damper 2 has substrate 18, can rotate around rotation axis 16 in circumferencial direction 12,14.Substrate
18 are formed as, for example, plate shape or double plate shapes, wherein substrate 18 is preferably in radial direction 8,10 place planes, drawing herein
Extend in plane processed.Substrate 18 can rotatably be fixedly attached to the portion in transmission system for example in the region of rotation axis 16
Part, to mitigate the rotation vibration of element.Substrate 18 is rotatably fixed the component for being installed to transmission system, below in reference to figure
5 pairs its be more fully described.
Torsional vibration damper 2 further has inertia mass part 20, and wherein inertia mass part 20 is formed as annular.Inertia
Mass member 20 is supported in radial direction 8 via at least three rollers 22 or can be supported on substrate 18.Therefore, roller 22 is in circle
It is separated from each other in circumferential direction 12,14 with unified distance.In the shown embodiment, roller 22 is fixed to inertia mass in the following manner
Part 20: it can be rotated relative to substrate 18 on circumferencial direction 12,14 with inertia mass part 20 together.Therefore, can illustrate, roller 22
It is set as being fixed on inertia mass part 20 on circumferencial direction 12,14.However, roller 22 is removably secured to inertia mass part
On 20.Therefore, the roll axis 24 that each of roller 22 can extend around in the axial direction 4,6 rotates.On the contrary, roller rail 26 is arranged in base
On part 18, roller 22 can roll on it, preferably on the outside on 28.Substrate 18 has maximum radius r1, can be designated as
The maximum radius of substrate 18, central roll rail 26 are set as the outside of the circumference 30 in radial direction 8, radius r2For substrate 18
Maximum radius r180%, be when necessary 90%.In an illustrated embodiment, the maximum radius r of substrate 18 is arranged in roller rail 261's
At level.Addedly, in the point referring to the fact: reversed arrangement is also feasible.Therefore, roller 22 can also or addedly rotatably
It is fixed on substrate 18, and roller rail 26 is arranged on inertia mass part 20, roller 22 can roll on it.Therefore, in the embodiment
In deformation, roller rail 26 may be alternatively provided as 18 outside of substrate or maximum radius r in radial position 81Circumference outside.
Inertia mass part 20 is further supported at least one axial direction 4,6 via at least one roller 22 or into one
Step can be supported on substrate 18, preferably on two axial directions 4 and 6.Therefore, first embodiment shown in Fig. 3 becomes
In shape, the outside 28 for the roller 22 that at least one is fixed on inertia mass part 20 or substrate 18, substrate is arranged in peripheral groove 32
18 extend into the peripheral groove 32 in radial direction 8, to realize that inertia mass part 20 is forced to lock on 4,6 in the axial direction
Surely it is fixed on substrate 18.Therefore deformation being shown in FIG. 3, central roll 22 is rotatably secured on inertia mass part 20, and
Roller rail 26 is arranged on substrate 18.Alternatively or supplementarily, groove 34 may be provided on substrate 18 or inertia mass part 20, wherein
Fig. 4 shows second embodiment deformation.In second embodiment deformation, roller 22 extends such as substrate 18 in radial direction 10 or is used to
In groove 34 on property amount part 20, wherein Fig. 4 also shows that embodiment, and central roll 22 is rotatably secured to inertia mass part 20
On, and roll shaft 26 is arranged on substrate 18.The point referring again to: can be with similar according to the deformation of the two of Fig. 3 and 4 embodiments
Mode is used for a pattern, is rotatably secured on substrate 18 in the pattern central roll 22, and roller rail 26 is arranged in inertia mass part
On 20.
Can be obtained from Fig. 1, torsional vibration damper 2 further have resetting apparatus 36, be set as just opposite to each other and/
Or it is separated from each other on the circumferencial direction 12,14 in torsional vibration damper 2 with unified distance.Therefore, resetting apparatus 36 is set
It is calculated as essentially identical in structure, is referred to one of resetting apparatus 36 in this way resetting apparatus 36 is described below, wherein should
Description is equally applicable to other resetting apparatuses 36.Referring again to the fact: torsional vibration damper 2 can unquestionably have three
The resetting apparatus 36 of a or multiple type described below, wherein these resetting apparatuses 36 also should be on circumferencial direction 12,14 with system
One distance is separated from each other.
Resetting apparatus 36 has the spring unit 38 and pivotable lever element 40 for generating setting power, passes through as a result,
Generate the reset force that inertia mass part 20 is influenced via the reset force junction 44 of lever element 40, the setting power of spring unit 38
Inertia mass part 20 can be transmitted to from the setting power junction 42 of lever element 40.In other words, inertia mass part 20 can be against multiple
Position device 36 reset force and around rotation axis 16 circumferencial direction 12,14 relative to substrate 18 rotate.
Lever element 40 can be pivoted relative to substrate 18 around fixed pivotal point 46.Therefore, lever element 40 can be relative to
The pivot axis that substrate 18 extends around in axial direction 4,6 pivots.Therefore, pivotal point 46 can be by protrusion outstanding on substrate 18
It is formed.Displaced path 48 that pivotal point 46 can extend along the straight line in the axial direction 8,10 and moved relative to substrate 18
Position, wherein to form displaced path 48, for example, being used to form the correspondence guide body of the protrusion protrusion of pivotal point 46 may be provided at
On substrate 18.If pivotal point 46 is also formed by such prominent protrusion on substrate 18, protrusion is preferably in the axial direction
4, extend in the guide body 50 on the lever element 40 on the extending direction of 6 lever element 40, and be formed as elongated recesses.
Lever element 40, which has, is transmitted to lever element from spring unit 38 in the point in setting power junction 42(setting power
40) the first lever segment 52 between pivotal point 46.In addition, lever element 40 has the second lever segment 54, pivoting
Extend between point 46 and reset force junction 44, wherein there is reset force caused by the setting power of spring unit 38 to connect by reset force
Chalaza 44 influences inertia mass part 20.First lever segment 52 has length l1, and the second lever segment 54 has length l2.Cause
This, lever element 40 has lever ratio l1/l2, i.e. l1Compare l2。
As shown in Fig. 2, rotating inertial mass part 20, two length l and around rotation axis 16 relative to substrate 181
And l2It is changeable, thus increase or or reduce, basic holding lever ratio l1/l2.For this purpose, as shown in the Examples, a side
Face, pivotal point 46 can be shifted relative to lever element 40, such as prominent above with reference to the protrusion for forming pivotal point 46 and guide body 50
The description risen.On the other hand, reset force junction 44 can be moved on the extending direction of lever element 40 relative to lever element 40
Position.Since guide body is arranged in lever element 40 in the protrusion protrusion on the inertia mass part 20 for forming reset force junction 44
On 56, the latter is achieved, and wherein conduit 56 extends on the extending direction of lever element 40 as guide body 50, and shape
Become, for example, the elongated recesses on lever element 40.On the contrary, setting power connects when lever element 40 is pivoted around pivotal point 46
Chalaza 42 keeps its setting relative to lever element 40.However, at least setting junction 42 may be configured as relative to lever member
The extending direction of part 40 is fixed on lever element 40.Even if illustrated embodiment is preferably, alternatively, to pass through and change lever portion
Divide 52,54 length l1、l2, pivotal point 46 and setting power junction 42 are formed as to answer relative to the movement of lever element 40
Position power junction 44 keeps its setting relative to lever element 40.In this example embodiment, guide body 56 may specify that setting power connects
Chalaza 42.The supporting track and roller unit being then described below in detail can also omit.
The reset force indicatrix that the reset force of inertia mass part 20 can be influenced by changing, adjusts resetting apparatus 36.?
In illustrated embodiment, for this purpose, the lever ratio l of lever element 401/l2It is alterable, this is because: pivotal point 46 can be along
Above-mentioned displaced path 48 is inwardly adjusted or is shifted outward or in radial direction 10 relative to 18 probe radial direction 8 of substrate, and
Change the lever ratio l of lever element 401/l2.For this purpose, settable corresponding resetting apparatus, can be along displaced path
48 adjust or shift pivotal point 46 in a manner of mechanical or waterpower, wherein for the purpose clearly expressed, resetting apparatus in attached drawing
Expression can be omitted.In any example, the reset force indicatrix of the reset force of inertia mass part 20 is influenced by changing, it is multiple
The controllability of position device 36 leads to torsional vibration damper 2 to the corresponding to adjustment of resetting apparatus 36 and neatly to biography
The different conditions of dynamic system or torsional vibration damper 2 are made a response.
The lever mass part 60 that lever element 40 has elongate lever part 58 and is arranged on lever piece 58.Lever piece 58 has
There is mass center 62 and lever mass part 60 has mass center 64.Therefore, lever mass part 60 is arranged in the following manner on lever piece 58:
Lever element 40(is made of lever piece 58 and lever mass part 60) mass center 66 be arranged in radial direction 8 than lever piece 58
The more outside position of mass center 62.Lever mass part 60 can be inherently created with lever piece 58.Alternatively, lever mass part 60 can
It separates and is formed with lever piece 58, to removably or be unreleasably fastened to lever piece 58 via fastener or fastening point
On.The lever mass part 60 formed about initial separation, it is further preferred that, lever mass part 60 is determined on lever piece 58
Position can be changed at least on the extending direction of radial direction 8,10 or lever piece 58, to realize lever element 40(by lever matter
Part 60 and lever piece 58 is measured to form) mass center 66 appropriate setting.
The mass center 66 of lever element 40 is set as in radial direction 8, may be in the level at setting power junction 42, can also
It can be as illustrated in fig. 1 and 2 on the position more more outside than setting power junction 42 of radial direction 8.More precisely, mass center 66 is set
It is set to the position more more outside than pivotal point 46 in radial direction 8.Due in the shown embodiment, passing through change reset force feature
Curve, pivotal point 46 can be shifted or be moved in radial direction 8,10 along displaced path 48, be contemplated that: lever element 40
Mass center 66 is set as at least on the setting position of pivotal point 46, in radial direction 8 than the pivotal point 46 on the setting position
More outside position.However, it is also preferred that pivotal point is compared in the setting of mass center 66 of lever element 40 in radial direction 8
46 more outside positions, no matter the corresponding setting position of pivotal point 46.However, it is also possible that clear in the following manner
The mass center 66 of lever element 40: radial direction 8 be located at its most external setting position pivotal point 46 setting radial direction 8,
In the level of the mass center 66 of 10 lever element 40.In the shown embodiment, mass center 66 is not only set as comparing pivot in radial direction 8
The more outside position of turning point 46, no matter the setting position of pivotal point 46, and the mass center 66 of lever element 40 is arranged in radial direction
The position more more outside than reset force junction 44 of direction 8, wherein it is also possible that the mass center 66 of lever element 40 is arranged
In radial direction 8,10 in the level at reset force junction 44.It is set by using the mass center 66 of above-mentioned substitution lever element 40
It sets, the influence that the centrifugal force of lever element 40 is influenced in the case where torsional vibration damper 2 is in higher rotational can optimize or change
Become, to realize: being based only upon centrifugal force, lever element 40 has tended to return to initial position shown in FIG. 1, wherein by Fig. 1 and
The setting of mass center 66 more more outside than reset force junction 44 in radial direction 8 shown in 2, the behavior is with a kind of special
Degree is supported.It can also be obtained from Fig. 1 and 2, when from axial direction 4,6, the setting of mass center 66 of lever element 40 exists
In the common linear 68 of pivotal point 46, reset force junction 44 and setting power junction 42, wherein the straight line 68 is preferably right
It should be according to the radial line on the initial position of the lever element 40 of Fig. 1.In any example, the mass center 66 of lever element 40 should be set
It sets at least and in the common linear 68 at pivotal point 46 and setting power junction 42.
Lever element 40 is in radial direction 8 and radial direction 10, and side is via in the supporting track 70,72 on substrate 18
At least one, the other side via the rotational roller unit 74 that can be rolled on substrate 18 along supporting track 70,72, be supported or
It can be supported on substrate 18.More precisely, by rotating inertial mass part 20, power junction 42 is arranged can be along supporting rail
Road 70,72 is mobile relative to substrate 18.As shown in the Examples, at setting power junction 42, roller unit 74 is rotatably secured to
On lever element 40.Therefore, roller 74 shown in embodiment is formed as roller bearing, it is therefore preferable to which needle bearing, inside race 76 are pacified
Dress is fixed in the protrusion protrusion for forming the lever element 40 at setting power junction 42, wherein roller element 78 is arranged in roller bearing
Inside race 76 and outer race 80 between, and outer race 80 can be supported and be rolled on above-mentioned supporting track 70,72.
In the form of roller bearing formed roller unit 74 setting is here formed as in guide body 82(as elongated recesses) on, only with
Dash line is shown as part 84, and wherein part 84 can inherently create or can be used as independent part with substrate 18 and be fixed on substrate 18
On.Supporting track 70 is outwardly formed the boundary of guide rail 82 in radial direction 8, and supporting track 72 indicates in radial direction 10
The boundary of inside conduit 82.Due to roller unit 74, the lever element 40 in side and setting between the substrate 18 in the other side
The abrasion for setting the region at power junction 42 (can be when lever element 40 pivots or when inertia mass part 20 be rotated relative to substrate 18
Occur) it substantially reduces.In the point it should be noted that roller unit 74 can also be designed particularly simple, thus, for example being formed as to revolve
The wheel or rotatable roller turned, is supported or can be supported on corresponding supporting track 70,72.Shown in it shall yet further be noted that
Setting can also be realized reversely, in this way, the guide body 82 including supporting track 70,72 is arranged on lever element 40, and roller unit
74 may be provided on substrate 18.
There are two helical springs 86,88 for the tool of spring unit 38 of resetting apparatus 36, and formed here is helical compression bullet
Spring.Two springs 86,88 act on each other on the setting power junction 42 of lever element 40 or lever element 40.Therefore, two
Helical spring 86,88, such as via the support baseboard for being formed as end bottom plate, correspondingly side is supported on the support on substrate 18
On point 90,92, the other side is supported on setting power junction 42.Therefore, two helical springs 86,88 are correspondingly disposed in substrate
In 18 recess portion 94, wherein the recess portion 94 for helical spring 86,88 is preferably formed to continuous recess portion 94.Recess portion 94 has respectively
There is the support-side 96 for inwardly corresponding to helical spring 86,88 in radial direction 10 substantially.Therefore, helical spring 86,88 passes through
It is arranged on the outside helical spring 86,88 of radial direction 8 in support-side 96 by support baseboard 98() it is respectively supported or divides
It can not be supported.From Fig. 1 and 2, it can be concluded that, support baseboard 98 is respectively formed as end each in helical spring 86,88
Portion's bottom plate, wherein support baseboard 98 forms the support baseboard for being used for a helical spring 86 and for another helical spring 88
Support baseboard.In the shown embodiment, support baseboard 98 is formed as an entirety, and is preferably made of plastics.
Support baseboard 98 has central part 100, and two helical springs 86,88 between helical spring 86,88 are arranged in
Extending direction on.In addition, support baseboard 98 has the first part 102 for being connected to central part 100 and is connected to central part
Divide 100 second part 104, first part extends between the periphery and support-side 96 of helical spring 86, and second part is therefrom
Center portion point 100 starts to extend between the periphery and support-side 96 of helical spring 88.In other words, first part 102 is arranged in spiral shell
Revolve spring 86 periphery and support-side 96 between, and second part 104 be arranged in helical spring 88 periphery and support-side 96 it
Between.In this process, in the supporting point of corresponding support-side 96 and side support baseboard 98 and other side helical spring 86,88
90, gap 106 is generated between the periphery of corresponding helical spring 86,88 in the region of the helical spring 86,88 between 92.Substantially
On, more support baseboards can be set in the recess portion 94 on corresponding helical spring 86,88, wherein gap 106 in this example embodiment
It can also be formed between the support baseboard 98 of side and the additional support bottom plate of the other side.Gap 106 makes helical spring 86,88
It can be bent outwardly in radial direction 8 into gap 106 with higher rotational, and corresponding helical spring 86,88 and correlation
It is not in contact between the support-side 96 of recess portion 94, in this way, helical spring 86,88 can realize its function in the clear, and
Abrasion on recess portion 94 and on corresponding helical spring 86,88 is avoided.
The setting power of the spring unit 38 formed by helical spring 86,88 is transmitted to setting power via support baseboard 98 and is connect
Chalaza 42.For this purpose, formed setting power junction 42 lever element 40 on protrusion can, for example, passing through support baseboard
Corresponding recess portion or opening on 98 and extend.No matter being correspondingly connected on setting power junction 42 of support baseboard 98, supports bottom
Plate 98 and lever element 40 are supported on or can be supported on the part 84 of substrate 18 via roller unit 74 and supporting track 70,72
On.In addition, support baseboard 98 is at a certain distance with support-side 96 or recess portion 94 in radial side in the region of central part 100
Inside side on to 10 is shown by the recess 108 on side of the central segment 100 towards support-side 96.Therefore, it supports
Bottom plate 98 is necessary when necessary also via the part of central part 100 and second part 104 substantially via first part 102
When also being partially supported upon in corresponding support-side 96 via central part 100, and central part 100 is to the branch of support baseboard 98
Support is substantially to realize via roller unit 74 and supporting track 70,72.In this way, being separately implemented at three branch being separated from each other
It supports, has proven to advantageous in support point.
Fig. 5 schematically shows the transmission system 110 for motor vehicles, wherein showing setting whirling vibration according to Fig. 1 to 4
The difference of damper 2 may.There is transmission system 110 gear unit 112, torque-vibration damper 114(can be designated as double matter
Measure flywheel, and follow gear unit 112 in torque flow), follow the clutch of torque-vibration damper 114 to fill in torque flow
It sets 116 and follows the speed changer 118. of arrangement of clutch 116 in torque flow therefore, torsional vibration damper 2(is in Fig. 5 point
Do not shown by dash line) input side 120, the twisting vibration of torque-vibration damper 114 can be rotatably secured to its substrate 18
The outlet side 122 of damper 114, the input side 124 of arrangement of clutch 116, arrangement of clutch 116 outlet side 126, speed changer 118
Input side 128 and/or speed changer 118 outlet side 130.Multiple torsional vibration dampers 2 of the above-mentioned type can be also used in biography
In transmission system 110 on point listed by the upper surface of in dynamic system 110.Arrangement of clutch 116 is preferably multiple disk arrangement of clutch,
The input side for being fixed on outlet side disc holder or input side or output is revolvably installed in the substrate 18 of middle torsional vibration damper 2
The radial support of the disc holder of side, in particular, in this manner it is achieved that torsional vibration damper 2 and disc holder or disc holder
Support section between joint reinforce.
Reference symbol table
2 torsional vibration dampers
4 axial directions
6 axial directions
8 radial directions
10 radial directions
12 circumferencial directions
14 circumferencial directions
16 rotation axis
18 substrates
20 inertia mass parts
22 rollers
24 roll axis
26 roller rails
28 outsides
30 circumference
32 peripheral grooves
34 grooves
36 resetting apparatuses
38 spring units
40 lever elements
42 setting power junctions
44 reset force junctions
46 pivotal points
48 displaced paths
50 guiding pieces
52 first lever segments
54 second lever segments
56 guiding pieces
58 lever pieces
60 lever mass parts
62 mass centers
64 mass centers
66 mass centers
68 straight lines/radial direction
70 supporting tracks
72 supporting tracks
74 roller arrangements
76 inside races
78 rolling elements
80 outer races
82 guiding pieces
84 parts
86 helical springs
88 helical springs
90 supporting points
92 supporting points
94 recess portions
96 support-sides
98 support baseboards
100 central parts
102 first parts
104 second parts
106 gaps
108 recess
110 transmission systems
112 gear units
114 torque-vibration dampers
116 arrangement of clutch
118 speed changers
120 input sides
122 outlet sides
124 input sides
126 outlet sides
128 input sides
130 outlet sides
l1Length
l2Length
r1Maximum radius
r2Radius of a circle
Claims (41)
1. a kind of torsional vibration damper (2), including can be around the substrate (18) that rotation axis (16) rotate and can be relative to
The substrate (18) and the inertia mass part (20) rotated against the reset force of resetting apparatus (36), wherein the resetting apparatus
(36) there is the spring unit (38) for generating setting power, wherein the resetting apparatus (36) has can be around pivotal point
(46) power is arranged from the lever element (40) via the lever element (40) at least one lever element (40) pivoted
Setting power junction (42) the inertia mass part (20) can be transmitted to, while the reset force is generated, via the thick stick
The reset force junction (44) of rod element (40) influences the inertia mass part (20), which is characterized in that the lever element
(40) side is via the supporting track (70 on the substrate (18) or the lever element (40)；It 72) and can be along described
The supporting track (70 on substrate (18) or the lever element (40)；72) roll rotational roller unit (74) radially
It is supported on the substrate (18).
2. torsional vibration damper (2) according to claim 1, it is characterised in that: the setting power junction (42) can
Along the supporting track (70 and rotating inertia mass part (20) relative to the substrate (18)；72) mobile.
3. torsional vibration damper (2) according to claim 1, it is characterised in that: the roller unit (74) is formed as roller
Bearing.
4. torsional vibration damper (2) according to claim 1, it is characterised in that: the roller unit (74) is formed as rolling
Needle bearing.
5. torsional vibration damper (2) according to claim 1, it is characterised in that: the spring unit (38), which has, to be used
In at least one helical spring (86 for generating setting power；88), the helical spring (86；88) it is arranged on the substrate (18)
Recess portion (94) in.
6. torsional vibration damper (2) according to claim 5, it is characterised in that: at least one displaceable support baseboard
(98) it is arranged in the helical spring (86；88) in the recess portion (94), via the support baseboard (98), the spiral bullet
Spring (86,88) is supported or can be supported on towards the helical spring (86 on radial direction (8)；One of 88) described recessed
In the support-side (96) in portion (94).
7. torsional vibration damper (2) according to claim 6, it is characterised in that: the support baseboard (98) is described
Extend between the periphery and the support-side (96) of helical spring (86,88).
8. torsional vibration damper (2) according to claim 7, it is characterised in that: while at the support bottom of side
The helical spring (86 on plate (98) and the substrate (18) of the other side；Other support baseboards 88) or supporting point (90,
92) helical spring (86 between；88) it generates in region in the support-side (96) and the helical spring (86；88)
Periphery between gap (106).
9. torsional vibration damper (2) according to claim 5, it is characterised in that: the setting of the spring unit (38)
Power can be transmitted to the setting power junction (42) and/or the support baseboard (98) via the support baseboard (98)
With the lever element (40) via the roller unit (74) and supporting track (70；72) it is supported or can be supported on the base
On part (18).
10. torsional vibration damper (2) according to claim 9, it is characterised in that: the support baseboard (98) with it is described
Lever element (40) is via the roller unit (74) and supporting track (70；72) it is supported or the setting power can be supported on and connect
In the region of chalaza (42).
11. torsional vibration damper (2) according to claim 5, it is characterised in that the spring unit (38) has two
It is a to be located at the helical spring (86,88) on the lever element (40) and interacted with each other.
12. torsional vibration damper (2) according to claim 11, it is characterised in that the support baseboard (98), which is formed, to be used
In helical spring (86) the support baseboard and be used for the support bottom of another helical spring (88)
Plate.
13. torsional vibration damper (2) according to claim 12, it is characterised in that the support baseboard (98) is formed as
One entirety.
14. torsional vibration damper (2) according to claim 13, it is characterised in that the support baseboard (98) is by plastics
It is made.
15. torsional vibration damper (2) according to claim 1, it is characterised in that: the mass center of the lever element (40)
(66) it is arranged in the level at the setting power junction (42) on radial direction (8) or on radial direction (8) than described
More outside or more more outside than the pivotal point (46) on radial direction (8) position in power junction (42) is set, wherein
The mass center (66) of the lever element (40) be set as when from axial direction (4,6) observe when with the pivotal point (46) and/
Or in the common linear (68) or common radial line of the reset force junction (44) and/or setting power junction (42).
16. torsional vibration damper (2) according to claim 15, it is characterised in that: the matter of the lever element (40)
In the level for the reset force junction (44) that the heart (66) is arranged on radial direction (8,10).
17. torsional vibration damper (2) according to claim 15, it is characterised in that: the matter of the lever element (40)
Position more more outside than the reset force junction (44) on radial direction (8) is arranged in the heart (66).
18. torsional vibration damper (2) according to claim 1, it is characterised in that: the lever element (40) has thick stick
Rod piece (58) and the lever mass part (60) being fixed on the lever piece (58), the mass center (66) of the lever element (40) are set
It is set to more more outside than the mass center (62) of the lever piece (58) on radial direction (8).
19. torsional vibration damper (2) according to claim 18, it is characterised in that: the lever mass part (60) with
The lever piece (58) inherently or is formed separately.
20. torsional vibration damper (2) according to claim 19, it is characterised in that: separated with the lever piece (58)
The lever mass part (60) that ground is formed removably or is unreleasably fastened to the lever piece (58) via fastening point
On.
21. torsional vibration damper (2) according to claim 1, it is characterised in that: the inertia mass part (20) can be through
By at least three rollers (22) in radial direction (8；10) it is supported or can be supported on the substrate (18) on, roller rail (26) is set
The circumference (30) being set on radial direction (8) is external, radius (r2) be the substrate (18) maximum radius (r1) 80%.
22. torsional vibration damper (2) according to claim 1, it is characterised in that: the inertia mass part (20) can be through
By at least three rollers (22) in radial direction (8；10) it is supported or can be supported on the substrate (18) on, roller rail (26) is set
The circumference (30) being set on radial direction (8) is external, radius (r2) be the substrate (18) maximum radius (r1) 90%.
23. the torsional vibration damper according to claim 21 or 22 (2), it is characterised in that: (22) one sidespin of roller
It is fixed on the inertia mass part (20) or the substrate (18) with turning, and the other side can be in the substrate (18) or described
Inertia mass part rolls on (20).
24. the torsional vibration damper according to claim 21 or 22 (2), it is characterised in that: the roller (22) can be in institute
It states and is rolled on the roller rail (26) on substrate (18) or the inertia mass part (20).
25. torsional vibration damper (2) according to claim 21, it is characterised in that: the roller rail (26) is arranged in institute
State the maximum radius (r of substrate (18)1) on.
26. torsional vibration damper (2) according to claim 21, it is characterised in that: inertia mass part (20) warp
By at least one roller (22) at least one axial direction (4；6) it is further supported on or can further be supported.
27. torsional vibration damper (2) according to claim 26, it is characterised in that: inertia mass part (20) warp
It is further supported on two axial directions (4,6) by least one roller (22) or can be further supported.
28. torsional vibration damper (2) according to claim 26, it is characterised in that: peripheral groove (32) is arranged extremely
Outside (28) in a few roller (22) being fixed on the inertia mass part (20) or substrate (18), the substrate (18) or
The mass member (20) extends into the peripheral groove (32) or groove is arranged in the substrate (18) or the inertia mass
In part (20), the roller (22) is extended into the groove.
29. torsional vibration damper (2) according to claim 1, it is characterised in that: the lever element (40) has
It is described setting power junction (42) and the pivotal point (46) between the first lever segment (52) and in the pivotal point
(46) the second lever segment (54) between the reset force junction (44), length (l1, l2) can be by relative to described
Substrate (18) rotates the inertia mass part (20) and changes, while keeping lever ratio (l substantially1/l2).
30. torsional vibration damper (2) according to claim 29, it is characterised in that: by changing the lever segment
Length (the l of (52,54)1, l2), the pivotal point (46) and the reset force junction (44) can be relative to the levers
Element (40) is mobile, and the setting power junction (42) keeps its being oppositely arranged relative to lever element (40).
31. torsional vibration damper (2) according to claim 29, it is characterised in that: by changing the lever segment
Length (the l of (52,54)1, l2), the pivotal point (46) and the setting power junction (42) can be relative to the levers
Element (40) is mobile, and the reset force junction (44) keeps its being oppositely arranged relative to lever element (40).
32. torsional vibration damper (2) according to claim 1, it is characterised in that: the resetting apparatus (36) can pass through
Change the reset force indicatrix of the reset force and adjusts.
33. torsional vibration damper (2) according to claim 32, it is characterised in that: the institute of the lever element (40)
State lever ratio (l1/l2) it is that can change.
34. torsional vibration damper (2) according to claim 33, it is characterised in that: the pivotal point (46) can pass through
Change the lever ratio (l of the lever element (40)1/l2) and adjust.
35. torsional vibration damper (2) according to claim 32, it is characterised in that: the matter of the lever element (40)
The heart (66) is set as at least on the setting position of the pivotal point (46), or than the pivotal point on radial direction (8)
(46) setting position of the more outside position but regardless of the pivotal point (46).
36. a kind of for the biography with the motor vehicles of torsional vibration damper (2) described in one of with good grounds preceding claims
Dynamic system (110), the substrate (18) are rotatably fixedly mounted on the component of the transmission system (110).
37. transmission system (110) according to claim 36, it is characterised in that: the component is torque-vibration damper
(114) or the outlet side (122) of the input side of double mass flywheel (120), torque-vibration damper (114) or double mass flywheel,
The input side (124) of arrangement of clutch (116).
38. transmission system (110) according to claim 36, it is characterised in that: the component be input side disc holder, from
Attach together the input side (128) of the outlet side (126), speed changer (118) of setting (116) and/or the outlet side of speed changer (118)
(130).
39. transmission system (110) according to claim 36, it is characterised in that: the component is input side disc holder
Radial support.
40. the transmission system according to claim 38 (110), it is characterised in that: the arrangement of clutch (116) it is described defeated
Side (126) are outlet side disc holders out, and the substrate (18) is rotatably fixedly installed in this, while increasing outlet side disc holder
Engine speed intensity.
41. the transmission system according to claim 38 (110), it is characterised in that: the arrangement of clutch (116) it is described defeated
Side (126) are the radial supports of outlet side disc holder out, and the substrate (18) is rotatably fixedly installed in this, are increased simultaneously
The engine speed intensity of the radial support of outlet side disc holder.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102014016573.6 | 2014-11-08 | ||
| DE102014016573.6A DE102014016573A1 (en) | 2014-11-08 | 2014-11-08 | Torsional vibration damper and drive train for a motor vehicle with such a torsional vibration damper |
| PCT/US2015/059449 WO2016073842A1 (en) | 2014-11-08 | 2015-11-06 | Rotational vibration damper and drive train for a motor vehicle with a rotational vibration damper of this type |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107002816A CN107002816A (en) | 2017-08-01 |
| CN107002816B true CN107002816B (en) | 2019-10-22 |
Family
ID=55802775
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580059844.6A Active CN107002816B (en) | 2014-11-08 | 2015-11-06 | The transmission system of torsional vibration damper and the motor vehicles for having the torsional vibration damper |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP3215758A4 (en) |
| CN (1) | CN107002816B (en) |
| DE (1) | DE102014016573A1 (en) |
| WO (1) | WO2016073842A1 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102016011143A1 (en) | 2016-09-15 | 2018-03-15 | Borgwarner Inc. | Torsional vibration damper, torsional vibration damper with such a torsional vibration damper and drive train with such a torsional vibration damper |
| DE102017007810A1 (en) * | 2016-10-24 | 2018-04-26 | Borgwarner Inc. | Torsional vibration damper and drive train for a motor vehicle with such a torsional vibration damper |
| DE102017000375A1 (en) | 2017-01-17 | 2018-07-19 | Daimler Ag | Torsional vibration damper for a drive train of a motor vehicle |
| CN108119605B (en) * | 2017-12-22 | 2019-09-03 | 宁波宏协股份有限公司 | A kind of double mass flywheel with sliding shoe formula centrifugal pendulum |
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| US4160390A (en) * | 1977-06-16 | 1979-07-10 | Spaetgens Theodore W | Tuned torsional vibration damper |
| DE19907216C1 (en) * | 1999-02-19 | 2000-10-12 | Univ Hannover | Torsional vibration damper |
| DE102012212854A1 (en) * | 2011-08-08 | 2013-02-14 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper for use in drive train of motor car, has molding body supported around rotation axis of drive shaft, and crank gear arranged between shaft and body and provided with centrifugal force-afflicted flywheel mass |
| CN103827541A (en) * | 2011-11-23 | 2014-05-28 | Zf腓特烈斯哈芬股份公司 | Torsional vibration damper assembly, in particular for the drive train of a motor vehicle |
| DE102014001016A1 (en) * | 2013-02-18 | 2014-08-21 | Borgwarner Inc. | Torsional vibration damper for internal combustion engine, has rotatable mass element arranged at input side or output side against restoring force of restoring device relative to input side or output side |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102007022891A1 (en) * | 2007-05-14 | 2008-11-20 | Borgwarner Inc., Auburn Hills | Shoe with a spring position limitation or torsional vibration damper with such a shoe |
| DE102009007373A1 (en) * | 2009-02-04 | 2010-08-05 | Magna Powertrain Ag & Co Kg | Dual Mass Flywheel |
| KR101344917B1 (en) * | 2012-11-28 | 2013-12-27 | 한국파워트레인 주식회사 | Torque converter for vehicle |
-
2014
- 2014-11-08 DE DE102014016573.6A patent/DE102014016573A1/en active Pending
-
2015
- 2015-11-06 WO PCT/US2015/059449 patent/WO2016073842A1/en active Application Filing
- 2015-11-06 EP EP15857906.0A patent/EP3215758A4/en not_active Withdrawn
- 2015-11-06 CN CN201580059844.6A patent/CN107002816B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4160390A (en) * | 1977-06-16 | 1979-07-10 | Spaetgens Theodore W | Tuned torsional vibration damper |
| DE19907216C1 (en) * | 1999-02-19 | 2000-10-12 | Univ Hannover | Torsional vibration damper |
| DE102012212854A1 (en) * | 2011-08-08 | 2013-02-14 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper for use in drive train of motor car, has molding body supported around rotation axis of drive shaft, and crank gear arranged between shaft and body and provided with centrifugal force-afflicted flywheel mass |
| CN103827541A (en) * | 2011-11-23 | 2014-05-28 | Zf腓特烈斯哈芬股份公司 | Torsional vibration damper assembly, in particular for the drive train of a motor vehicle |
| DE102014001016A1 (en) * | 2013-02-18 | 2014-08-21 | Borgwarner Inc. | Torsional vibration damper for internal combustion engine, has rotatable mass element arranged at input side or output side against restoring force of restoring device relative to input side or output side |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107002816A (en) | 2017-08-01 |
| WO2016073842A1 (en) | 2016-05-12 |
| EP3215758A4 (en) | 2018-07-18 |
| DE102014016573A1 (en) | 2016-05-12 |
| EP3215758A1 (en) | 2017-09-13 |
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