CN107208735B - Torsional vibration damper - Google Patents
Torsional vibration damper Download PDFInfo
- Publication number
- CN107208735B CN107208735B CN201680008419.9A CN201680008419A CN107208735B CN 107208735 B CN107208735 B CN 107208735B CN 201680008419 A CN201680008419 A CN 201680008419A CN 107208735 B CN107208735 B CN 107208735B
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- Prior art keywords
- output
- flange
- stop part
- vibration damper
- torsional vibration
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- 239000011159 matrix material Substances 0.000 claims description 10
- 238000013016 damping Methods 0.000 claims description 5
- 238000005056 compaction Methods 0.000 claims description 4
- 230000009977 dual effect Effects 0.000 abstract 1
- 238000002485 combustion reaction Methods 0.000 description 11
- 230000007246 mechanism Effects 0.000 description 8
- 238000000034 method Methods 0.000 description 5
- 230000010355 oscillation Effects 0.000 description 5
- 238000004146 energy storage Methods 0.000 description 4
- 239000006096 absorbing agent Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000005457 optimization Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000035939 shock Effects 0.000 description 3
- 230000006978 adaptation Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000005284 excitation Effects 0.000 description 2
- 239000004744 fabric Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000000737 periodic effect Effects 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
- F16F15/1217—Motion-limiting means, e.g. means for locking the spring unit in pre-defined positions
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
A torsional vibration damper (100), in particular a dual mass flywheel, has an input part (102) and an output part (104) with a common rotational axis (106) about which the input part (102) and the output part (104) can be rotated jointly and can be rotated in a limited manner relative to one another, and the torsional vibration damper has a spring damper arrangement with at least one energy store (108) acting between the input part (102) and the output part (104), and the torsional vibration damper has a secondary stop arrangement, wherein the input (102) and the output (104) each have a respective secondary stop (118, 120, 124, 126), in the torsional vibration damper, the secondary stop (118, 120) of the input part (102) and/or the secondary stop (124, 126) of the output part (104) is formed by at least one additional flange (128).
Description
Technical field
The present invention relates to a kind of torsional vibration damper, especially double mass flywheel, the torsional vibration damper is included with common
The input component and output of pivot center, the input component and output can be rotated together around the pivot center and energy
It is enough limitedly to reverse relative to each other；The spring cushion device to work between input component and output, the spring damping
Device has at least one accumulator；And secondary stop device, wherein input component and output are respectively provided with corresponding secondary
Stop part.
Background technique
From flanged component a kind of known to 195 22 718 A1 of DE, for being loaded at least two helical springs
Force-storing device, the helical spring around the component concentric arrange, and in the direction of the helical spring
The arm of the component extended in radial directions is respectively disposed between mutual end, wherein the arm is (in the axial direction
On see) be for example arranged on shell between the supporting zone for helical spring, wherein the arm can not only load utilization
One in the helical spring of end toward each other, and another can be loaded, in the component, the arm is for one
Loading direction is implemented in the same manner, and has the shape different from other arm at least one arm of another loading direction, with
Just it is rigidly reduced in the case where being transitioned into coast region by the transition that elasticity and vibration damping resistance generate as low as possible
Level on, and spring is also made to keep underload under stress conditions herein, the stress is compacted by the spring
(auf Block) is generated.
It is with driving side and slave end from a kind of torsional vibration damper known to 10 2,008 009 656 A1 of DE
Transmitting element, the transmitting element can reverse relative to each other against at least one set between them vibration absorber,
The vibration absorber has at least one long helix spring to work in the circumferential, wherein transmitting element, which has, is used for spiral
The loading area of spring and helical spring inner radial is provided at least one stop element, at least one backstop member
Part is limited in the torsion between transmitting element, wherein the stop element helical spring maximum allowable compression travel it
Preceding 2 to 10 degree works, to protect the vibration absorber to work between two transmitting elements (to be especially made of helical spring
Accumulator) with antioverloading.
From torsional vibration damper, especially divided flywheel a kind of known to 10 2,008 018 218A1 of DE, have just
Grade flywheel mass and secondary flywheel mass, the primary flywheel mass can be connect with the drive shaft anti-torsion of internal combustion engine, institute
It states secondary flywheel mass and resists the resistance of at least two energy storage devices to work in circumferential direction in lead and inertia
It can be reversed relative to primary flywheel mass on line of travel, there is the primary flywheel mass primary for energy storage device to stop
Blocking means, wherein the primary stop device for energy storage device includes the overload protection arrangement to work in lead, institute
Overload protection arrangement is stated to be arranged in together with primary stop device in the common reception space for energy storage device.
Summary of the invention
The present invention is based on following tasks: improving the torsional vibration damper that introductory song is previously mentioned in structure and/or in function.Especially
Accumulator is avoided to fail.Especially arc spring is avoided to fail.It especially to avoid or at least minimize in the case of an overload
The damage of component.Especially to ensure the mobility of motor vehicle in the case where accumulator fails.Especially to prevent motor vehicle due to
Torsional vibration damper damages and stops (Liegenbleiben).Especially to prevent driving system from interrupting.Especially to optimize secondary stop part
Adaptation hit configuration.Especially to reduce the load due to caused by impact force.
The solution of the task is realized by a kind of torsional vibration damper, especially double mass flywheel, is included with common
The input component and output of pivot center, the input component and output can be rotated together around the pivot center and energy
It is enough limitedly to reverse relative to each other；The spring cushion device to work between input component and output, the spring damping
Device device has at least one accumulator；And secondary stop device, wherein input component and output are respectively provided with corresponding time
Grade stop part, in the torsional vibration damper, the secondary stop part of input component and/or the secondary stop part of output are by least one
A additional flange is constituted.
Since the secondary stop part of input component and/or the secondary stop part of output are made of at least one additional flange,
The rigidity of secondary stop part can be influenced in structure in other regions, thus in the case of an overload can to avoid or at least
Minimize the damage of component.The secondary stop part of output can be made of additional flange.The secondary stop part of output can be with
It is made of the additional flange of multi-piece type.The secondary stop part of output can be made of the additional flange of two-piece type.Input component
Secondary stop part can be made of additional flange.The secondary stop part of input component can be made of the additional flange of multi-piece type.It is defeated
The secondary stop part for entering part can be made of the additional flange of two-piece type.
The torsional vibration damper can be used for being arranged in the driving system of motor vehicle.The driving system can have internal combustion engine.It should
Driving system can have friction clutch device.Friction clutch device can have double clutch.Driving system can have change
Fast device.Speed changer can be dual-clutch transmission.Driving system can have at least one wheel that can be driven.Torsional oscillation vibration damping
Device can be used for being arranged between internal combustion engine and friction clutch device.Torsional vibration damper can be the portion of friction clutch device
Point.Torsional vibration damper can be used for reducing the torsional oscillation of the excitation of the periodic process by periodic process, especially in internal combustion engine.It turns round
Vibration damper can work on coast direction and/or in lead.Coast direction is to be directed toward internal combustion engine
Power flow direction.Lead is from the power flow direction of internal combustion engine.
The torsional vibration damper can be arranged in belt pulley decoupling device.Belt pulley decoupling device reduces in belt drive unit
Resonance, inhomogeneities and dynamic force.Belt pulley decoupling device can be connect in input component side with crankshaft.Belt pulley decoupling device can be with
It is connect in output side with belt pulley, the belt pulley for example drives auxiliary unit.
Input component and output can be supported in a manner of it can mutually reverse by means of bearing.Input component can be used for driving
The connection of dynamic side is especially connect with internal combustion engine.Output can be used for slave end connection, especially with friction clutch device
Connection.Term " input component " and " output " are for the power flow direction from internal combustion engine.
At least one accumulator can have at least one spring.At least one spring can be compression spring.At least one
A spring can be helical spring.At least one spring can be arc spring.At least one accumulator can be in coast
It works on direction and/or in lead.At least one accumulator can be acted as about pivot center with an operating radius
With.
At least one accumulator can be high capacity spring.High capacity spring is optimised in terms of possible shock.Only
It will be appreciated that hit, this for example in double mass flywheel when vehicle stops super torque in the case where gear formula load occurs.
Because being difficult to avoid hitting completely, it is necessary to stop shock by the fastness that torsional vibration damper increases.For this purpose, high capacity spring can
To make significant contribution.
At least one accumulator can be the arc spring with the spiral spacing increased.At least one accumulator can be
High capacity arc spring.High capacity arc spring has the spiral spacing increased.It is possible thereby to significantly increase stopping for arc spring
Keep off torque.High capacity arc spring can store about more 30% compared with conventional arc spring in the case where backstop does not occur
To 50% energy.The wire thickness of high capacity arc spring can be roughly equivalent to the wire thickness of conventional arc spring, from
And the strain of spring and service life thus remain unchanged.The specified spring rate of high capacity spring can be than conventional arc spring
Specified spring rate somewhat higher.High capacity arc spring helps avoid arc spring deformation.Double mass flywheel is by height
Capacity arc spring becomes firm and durable significantly, draws isolation performance (Zugisolation) without reducing.
Input component can have flange section.Input component can have cover region section.Flange section and cover region section can be mutual
It is permanently connected, especially welds.Flange section and cover region section can be connect with limit for the anchor ring formula of at least one the first accumulator
Receive space.
Output can have flange part.Additional flange can be connect with the flange part.Output can have flywheel matter
Measure part.Additional flange can be arranged in the axial direction between the flange part and the flywheel mass part.Flange part, additional flange
It can be fixedly connected to each other with flywheel mass part.Flange part, additional flange and flywheel mass part can be riveted mutually.Output
Flange part can be arranged in the axial direction between the flange section of input component and cover region section.Additional flange and cover region section can be with cloth
It sets on identical axial position.Flywheel mass part can be arranged in the axial direction cover region section on the side of flange section.
" in the axial direction " and " radially " direction explanation is for pivot center.The flywheel mass part of output can have
The overall diameter bigger than the operating radius of at least one accumulator.Spring cushion device can have rubbing device.
Input component can have primary stop part.Flange section can have primary stop part.Cover region section can have just
Grade stop part.Primary stop part can be extend into reception space.The primary stop part of input component can be used in input component side
Support at least one described accumulator.The primary stop part of input component can be worn by means of flange section and/or cover region section
Logical position is constituted.The primary stop part of input component can arranged diametrically opposed to each other.The flange part of output can have
There is primary stop part.The flange part of output can have the flange wing being extend into reception space to radially outer.The method
Lan Yi may be constructed the primary stop part of output.The primary stop part of output can be used in the collateral support at least one of output
A accumulator.The primary stop part of output can arranged diametrically opposed to each other.At least one accumulator can be with a side
Face is supported on the primary stop part of input component and is on the other hand supported on the primary stop part of output.
Input component can have secondary stop part.The secondary stop part of input component side can be arranged in cover region section.Cover region
Section, which can have, leaves a blank, and the secondary stop part of input component side is extend into described leave a blank, and the secondary stop part of output side
It is arranged in described leave a blank.Output can have the secondary stop part of output side.The secondary stop part of output side can be with
It is arranged in additional flange.When being more than the predetermined maximum torsion angle between input component and output, input component side
Secondary stop part and the secondary stop part of output side can abut each other.The secondary stop part of input component side and output
The secondary stop part of part side abuts each other that can also be considered as secondary stop part works.When reaching maximum torsion angle,
The preferably also non-load of at least one accumulator is to compaction state.The secondary stop part of input component and the secondary stop part of output
It can contact with each other, and accumulator is not clamped to compaction state.This minimizes or is avoided the damage of accumulator.In addition,
Sliding block can be clipped in the spiral of arc spring.
Secondary stop part can be arranged on backstop radius.Backstop radius can be less than the effect half of at least one accumulator
Diameter.Secondary stop part can be respectively diametrically mutually opposed.The secondary stop part of input component side can be respectively in diametrically phase
It is mutually opposed.The secondary stop part of output side can be respectively diametrically mutually opposed.The secondary stop part of input component side can be with
It is centrally disposed in respectively in the circumferential direction of input component between the primary stop part.The secondary stop part of input component side can
To be centrally disposed in respectively in the circumferential direction of input component between the primary stop part of cover region section side.
The secondary stop part of output side can be made of additional flange.Additional flange can be by least two flange section groups
At.The flange section can extend perpendicular to pivot center.The flange section can be implemented with level land.Flange section can be flat plate
Material.Flange section can be flat steel board.Additional flange can be made of lucky two flange sections.Two flange sections can be with mirror image
Symmetrically construct.Flange section can have matrix, the first backstop wing and the second backstop wing.First matrix of flange section can surround
The pivot center of torsional vibration damper constructs deviously.Flange section can have the through-hole for riveting with output.Flange section can
And have for output flange part and the riveting of flywheel mass part, through-hole in the base.Matrix is in circumferential direction
It can have two end regions, in the end regions, constriction and be transitioned into the backstop wing in radial directions.Only
Block wing can be flat.The backstop wing can be the finger-like region of flange section.The backstop wing can be to extend in general radial direction.Flange
Section can have lucky two backstop wings.
Additional flange can have lucky two flange sections, and the flange section is respectively provided with lucky two flange wings.Flange
One in the two flange wings of section can be referred to as the first flange wing.Another in the two flange wings of flange section can
To be referred to as the second flange wing.The first flange wing and the second flange wing of flange section can substantially be diametrically opposed to one another set and base
Body connection.The first flange wing and the second flange wing can be mirror symmetry.Two first of two flange sections of additional flange
The backstop wing can be disposed adjacently in circumferential direction.Two first backstop wings of two flange sections may be constructed time of output
Grade stop part.Two second backstop wings of two flange sections can be disposed adjacently in circumferential direction.The two of two flange sections
A second backstop wing may be constructed the secondary stop part of output.Since each in two secondary stop parts is by two backstop wings
It constitutes, secondary stop part is respectively provided with rigidity more smaller than the single type secondary stop part of identical size.Additional flange as a result,
Secondary stop part can avoid in the event of overloading or at least minimize the component damage in driving system.The end of the backstop wing
Portion can deviate from pivot center.The backstop wing can be arranged in plane identical with the secondary stop part of input component.Additional flange
The path of the backstop wing can be Chong Die with the path of secondary stop part of input component in radial directions, thus in input component and defeated
It is merely capable of limitedly relatively rotating between part out.
At least one of secondary stop part can be constituted so flexiblely, so that avoiding in the case of an overload or minimum
Change the damage of component, especially in the damage for driving the component in system for being disposed with torsional vibration damper.The secondary backstop of output side
Part can have the elastic bolster guide wing.The flange section of additional flange can have the elastic bolster guide wing.Secondary stop part can have respectively
There is the shape of stress optimization.The secondary stop part of output side can have the shape of stress optimization.
Generally and in other words, the present invention relates to a kind of with split type additional flange and high capacity groups of springs
The double mass flywheel of conjunction.The present invention includes leaving a blank in the lid of primary side, described to leave a blank with two or more stop parts.
It is fixed that on the secondary side, especially directly by main caulking part (it is contemplated that other fixed points), fixed, two-piece type flange is matched
It closes in leaving a blank in the lid.The two-piece type geometry and the elastic bolster guide wing of additional flange will generate as soft as possible stop
Block piece.In the case where maximally reversing, primary side can be reversed relative to primary side until backstop of the flange backstop in lid
On part.Two components are cast in this way by corresponding configuration so that against when also allow system determination residue rigidity.By
Remaining component of this protection in driving system is with antioverloading.
The present invention be may be mounted in double mass flywheel and damper and be mounted in belt pulley decoupling device.In this way
Mode avoid arc spring from failing: stop part protect arc spring to prevent its excess load, especially because caused by compaction state
Excess load.High capacity spring is preferably installed.In addition, the suitable configuration by component realizes following torsional rigids, the torsion
Turn the damage for the component that rigidity is minimized in the case of an overload in driving system.
Torsional vibration damper can have centrifugal pendulum mechanism.Centrifugal force pendulum can be used for the effect of improving torsional vibration damper.
Centrifugal pendulum mechanism can be arranged in the inner radial of at least one accumulator.Centrifugal pendulum mechanism can be arranged in the axial direction
Between the flange section and cover region section of input component.Centrifugal pendulum mechanism can be arranged on output.Centrifugal pendulum mechanism can be with
With pendulum mass frame member.The flange part of output can be used as the use of pendulum mass frame member.Centrifugal pendulum mechanism can have
At least one pendulum mass.At least one described pendulum mass can be on pendulum mass frame member along pendulum rail cloth in a manner of it can shift
It sets.At least one described pendulum mass can be displaced in running position under the action of the centrifugal force.In running position, it is described at least
One pendulum mass can be swung along pendulum rail, to absorb torsional oscillation.At least one described pendulum mass can be from middle position
It swings between two end positions.
In the case where torsional vibration damper does not have centrifugal pendulum mechanism, the stop part of additional flange can also input side with
Primary Flywheel disc collective effect.In the case where torsional vibration damper does not have centrifugal pendulum mechanism, stopper point, which also can be set, to be covered
On disk or on support plate.
By " can with " description especially optional feature of the invention.Therefore, following implementations of the invention are respectively present
Example, the embodiment have one or some corresponding features.
Accumulator is avoided to fail by torsional vibration damper according to the present invention.Particularly avoid arc spring failure.Especially exist
The damage of component is avoided or at least minimized under overload situations.Especially ensure the machine of motor vehicle in the case where accumulator fails
Dynamic property.Especially prevent motor vehicle from stopping since torsional vibration damper damages.Especially prevent driving system from interrupting.Especially optimization secondary is stopped
The configuration that the adaptation of block piece is hit.Especially reduce the load due to caused by impact force.
Detailed description of the invention
Explain the embodiment of the present invention in detail referring to the drawings.Other feature and advantage are obtained from the explanation.It should
The specific features of embodiment can show general characteristic of the invention.The feature of the embodiment combined with other feature can also
To show each feature of the invention.
It schematically and is exemplarily illustrated:
Fig. 1 shows the component week of torsional vibration damper in the state that secondary stop part works and in three-dimensional view
Side,
The flange section of the secondary stop part of the output side of Fig. 2 torsional vibration damper.
Specific embodiment
Fig. 1 shows torsional vibration damper 100.The torsional vibration damper 100 is used herein to be arranged in the driving system of motor vehicle
Between internal combustion engine and friction clutch device, such as double mass flywheel or double clutch damper.Torsional vibration damper 100
With input component 102 and output 104.Torsional vibration damper 100 has pivot center 106,104 energy of input component 102 and output
Enough rotates together and can limitedly reverse relative to each other around the pivot center.Input component 102 and output 104 it
Between, arc spring 108 works as accumulator.Here, there are two substantially semicircular arc-shaped arc bullets for the tool of torsional vibration damper 100
Spring 108.The arc spring 108 is embodied as high capacity spring and has the spiral spacing increased.In input component 102 and output
In the case that part 104 reverses relative to each other, 108 storage energy of arc spring releases energy in other words.In addition, rubbing device is defeated
Enter and works between part 102 and output 104.It is possible thereby to reduce torsional oscillation, the torsional oscillation is due to the periodicity in internal combustion engine
Process excitation.
Input component 102 has flange section 110 and cover region section 112.Cover region section 112 has annular disc shape.Flange
Section 110 and cover region section 112 are welded to each other.Flange section 110 and 112 limit of cover region section are used for the annulus planar of arc spring 108
Reception space.
Input component 102 have reach it is in the reception space, for input component it is collateral support arc spring 108 primary
Stop part.The primary stop part of input component 102 is arranged in opposed to each other on flange section 110 in the axial direction and cover region section
On 112.Here, there are two primary stop parts 114,116 for the tool of cover region section 112.Primary stop part 114,116 is diametrically mutually right
It arranges with setting.Primary stop part 114,116 is embodied as break-through position respectively.Primary stop part 114,116 is the office of cover region section 112
Portion region, the regional area are molded into reception space by the material of cover region section 112 against section arch respectively.
Input component 102 has secondary stop part 118,120.The secondary stop part 118,120 of input component 102 is arranged in cover region
In section 112.Here, there are two secondary stop parts 118,120 for the tool of cover region section 112.Secondary stop part 118,120 is diametrically mutual
It is opposed to arrange.Secondary stop part 118,120 be centrally disposed in the circumferential direction of cover region section 112 primary stop part 114,
Between 116.Here, secondary stop part 118,120 is arranged with being staggered 90 ° relative to primary stop part 114,116.Cover region section 112
It leaves a blank with largely circular.The circular shape left a blank is interrupted by secondary stop part 118,120.It is described to leave a blank
It is concentric relative to pivot center 106.Secondary stop part 118,120 is the finger portion being radially oriented, and the finger portion is in diameter
It is extended up in described leave a blank to side.Secondary stop part 118,120 is implemented with cover region section 112 at a ground.Secondary stop part
118, it 120 is more internally arranged radially than the operating radius of arc spring 108.In circumferential direction, two secondary backstop
Each of part 118,120 is by two stop surface limits.
The flywheel mass part that output 104 has flange part 122 and is not shown in the accompanying drawings.Flange part 122 has to diameter
The flange wing being extend into outside in reception space.The flange wing is used for as primary stop part in the collateral support arc of output
Spring 108.Flange part 122 and flywheel mass part mutually rivet in the case where being equipped with additional flange 128 in-between.
Here, output 104 has band, there are two the additional flanges 128 of secondary stop part 124,126.Therefore, output
104 secondary stop part 124,126 is made of additional flange 128.Additional flange 128 is arranged in flange part in the axial direction
It is riveted between 122 and flywheel mass part and with it.Additional flange 128 is made of two flange sections 130,132.Fig. 2 shows works
For the flange section 130 of single-piece.The mirror surface that the two flange sections 130,132 are arranged therein about pivot center 106 is mirror image pair
Claim.Each flange section 130,132 is made of 134,136, the first backstop wing 138,140 of matrix and the second backstop wing 142,144.
Each first matrix 134,136 is flat and constructs deviously around pivot center 106.Each two in matrix 134,146
A through-hole is used to rivet with flange part 122 and flywheel mass part.In circumferential direction, there are two ends for each tool of matrix 134,136
Portion region, in the end regions, described matrix in radial directions constriction and be transitioned into the backstop wing 138,140,142,
In one of 144.The backstop wing 138,140,142,144 is flat, finger-like the region of flange section 130,132, and the region is big
Cause extends in radial directions.The two first backstop wings 138,140 are circumferentially adjacently arranged and constitute output 104
Secondary stop part 124.Two second backstop wings 142,144 are disposed adjacently in circumferential direction and constitute output 104
Another secondary stop part 126.As a result, each of described two secondary stop parts 124,126 by two backstop wings 138,
140, it 142,144 constitutes, secondary stop part 124,126 has intensity more smaller than the single type secondary stop part of identical size.
Secondary stop part 124,126 can avoid in the case of an overload or at least minimize the damage of the component in driving system as a result,
It is bad.Secondary stop part 124,126 is more internally arranged radially than the operating radius of arc spring 108.Secondary stop part
124, it 126 is diametrically arranging opposed to each other.The end of the backstop wing 138,140,142,144 deviates from pivot center 106.Output
The secondary stop part 124,126 of part 104 and the secondary stop part 118,120 of input component 102 are arranged in the same plane.In radial direction
On direction, path and the input component 102 of the backstop wing 138,140,142,144 of the secondary stop part 124,126 of output 104
The path of secondary stop part 118,120 is overlapped, to be merely capable of between input component 102 and output 104 limitedly opposite
Rotation.
On the one hand arc spring 108 is supported on the primary stop part 114,116 of input component 102 and on the other hand supports
On the primary stop part of output 104.In the case where input component 102 and output 104 reverse relative to each other, arc spring
108 strike the beam relaxes in other words together.In normal operation, arc spring 108 is manipulated in its elastic range, input component
102 secondary stop part 118,120 and the secondary stop part 124,126 of output 104 are not in contact.It is being more than maximum internal combustion
When machine power square, input component 102 and output 104 are reversed relative to each other until following degree: being touched in the spiral of arc spring 108
Before, the secondary stop part 118,120 of input component 102 and the secondary stop part 124,126 of output 104 are in contact.Then,
In the case where arc spring 108 is not switched on therebetween, carried out between input component 102 and output 104 direct mechanical
Power transfer, torsional vibration damper 100 is rigidly attached, and arc spring 108 is not compacted.Arc spring 108 is less as a result,
Intensity ground load, and firmly (impact resistance) design in terms of shock of torsional vibration damper 100.
Reference signs list
100 torsional vibration dampers
102 input components
104 outputs
106 pivot centers
108 accumulators, arc spring
110 flange sections
112 cover region sections
114 primary stop part input component sides
116 primary stop part input component sides
118 grade stop part input component sides
120 grade stop part input component sides
122 flange parts
124 grade stop part output sides
126 grade stop part output sides
128 additional flanges
130 flange sections
132 flange sections
134 matrixes
136 matrixes
The 138 first backstop wings
The 140 first backstop wings
The 142 second backstop wings
The 144 second backstop wings
Claims (8)
1. torsional vibration damper (100), the torsional vibration damper include input component (102) with common rotation axis (106) and
Output (104), the input component (102) and the output (104) can rotate together around the pivot center and
It can limitedly reverse relative to each other；The spring damping to work between the input component (102) and the output (104)
Device device, the spring damper have at least one accumulator (108)；And secondary stop device, wherein the input
Part (102) and the output (104) are respectively provided with corresponding secondary stop part (118,120,124,126), which is characterized in that
The secondary stop part (124,126) of the output (104) is made of at least one additional flange (128), described additional
Flange (128) is made of two flange sections (130,132), and each flange section is by matrix, the first backstop wing and the second backstop wing group
It is connect with described matrix with setting at, the first backstop wing and the second backstop wing being diametrically opposed to one another, two first backstop wings are in circumferential direction
On be disposed adjacently and constitute one of output (104) secondary stop part (124), two second backstop wings are in circumferential direction
On be disposed adjacently and constitute another secondary stop part (126) of output (104).
2. torsional vibration damper (100) according to claim 1, which is characterized in that at least one described accumulator (108) is
High capacity spring.
3. torsional vibration damper (100) according to claim 2, which is characterized in that at least one described accumulator (108) is
The arc spring of spiral spacing with increase.
4. torsional vibration damper (100) according to claim 1, which is characterized in that in the feelings that the accumulator (108) pre-tighten
Under condition, the input component (102) can be reversed in so far relative to the output (104): until the input component
(102) the secondary stop part (124,126) of the secondary stop part (118,120) and the output (104) occurs
It contacts with each other, and the accumulator (108) is not clamped to compaction state.
5. torsional vibration damper (100) according to claim 1, which is characterized in that the input component (102) has flange
Section (110) and cover region section (112), also, be configured on the cover region section (112) input component side secondary stop part (118,
120)。
6. torsional vibration damper (100) according to claim 5, which is characterized in that the cover region section (112), which has, to be left a blank,
The secondary stop part (118,120) of the input component side is extend into described leave a blank, and the secondary backstop of the output side
Part (124,126) is arranged in described leave a blank.
7. torsional vibration damper (100) according to claim 1, which is characterized in that the output (104) has flange part
(122), and the additional flange (128) is connect with the flange part (122).
8. torsional vibration damper (100) according to claim 1, which is characterized in that the output (104) has flange part
(122) and flywheel mass part, also, the additional flange (128) is arranged in the flange part (122) in the axial direction and described flies
It takes turns between mass member.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102015203105.5 | 2015-02-20 | ||
| DE102015203105.5A DE102015203105B4 (en) | 2015-02-20 | 2015-02-20 | torsional vibration dampers |
| PCT/DE2016/200093 WO2016131457A1 (en) | 2015-02-20 | 2016-02-12 | Torsional vibration damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107208735A CN107208735A (en) | 2017-09-26 |
| CN107208735B true CN107208735B (en) | 2019-11-15 |
Family
ID=55484788
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201680008419.9A Active CN107208735B (en) | 2015-02-20 | 2016-02-12 | Torsional vibration damper |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP3259490A1 (en) |
| CN (1) | CN107208735B (en) |
| DE (2) | DE102015203105B4 (en) |
| WO (1) | WO2016131457A1 (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102018111162A1 (en) | 2017-05-17 | 2018-11-22 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper and method of manufacturing a torsional vibration damper |
| FR3069603B1 (en) * | 2017-07-28 | 2019-08-23 | Valeo Embrayages | TORSION SHOCK ABSORBER WITH ELASTIC END LIMIT STOP |
| FR3069602B1 (en) * | 2017-07-28 | 2020-08-28 | Valeo Embrayages | SHOCK ABSORBER WITH ELASTIC LIMIT STOP |
| FR3069600B1 (en) * | 2017-07-28 | 2020-07-03 | Valeo Embrayages | TORSION SHOCK ABSORBER WITH ELASTIC LIMIT STOP |
| WO2019020808A2 (en) * | 2017-07-28 | 2019-01-31 | Valeo Embrayages | Torsional vibration damper with elastic end-stop |
| DE102018104135B4 (en) * | 2018-02-23 | 2020-02-20 | Schaeffler Technologies AG & Co. KG | Pulley decoupler having a centrifugal pendulum device with a first friction device |
| DE102018108404A1 (en) | 2018-04-10 | 2019-10-10 | Schaeffler Technologies AG & Co. KG | torsional vibration dampers |
| DE102020121270A1 (en) * | 2019-09-02 | 2021-03-04 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper with centrifugal pendulum and pre-damper |
| DE102020202182A1 (en) | 2020-02-20 | 2021-08-26 | Zf Friedrichshafen Ag | Torsional vibration damper with angle of rotation limitation and clutch disc with torsional vibration damper |
| DE102021202297A1 (en) | 2021-03-10 | 2022-09-15 | Zf Friedrichshafen Ag | Vehicle, dual mass flywheel and torque transfer device |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1272601A (en) * | 1999-02-26 | 2000-11-08 | 易通公司 | Friction clutch with predamper |
| GB2413615A (en) * | 2004-05-01 | 2005-11-02 | Safe Developments Ltd | A clutch friction plate assembly |
| FR2918141A1 (en) * | 2007-06-26 | 2009-01-02 | Valeo Embrayages | TORSION OSCILLATION DAMPING DEVICE, IN PARTICULAR FOR A FRICTION CLUTCH, FOR EXAMPLE FOR A MOTOR VEHICLE. |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19522718B4 (en) * | 1994-07-01 | 2009-07-30 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | torsional vibration damper |
| JPH0949531A (en) * | 1995-08-08 | 1997-02-18 | Exedy Corp | Viscosity resistance generating mechanism |
| DE10133694A1 (en) * | 2000-07-27 | 2002-02-07 | Luk Lamellen & Kupplungsbau | Torsional vibration damper with transmission elements on both sides has intermediate element between control regions and circumferential ends of energy store |
| CN2871973Y (en) * | 2006-03-06 | 2007-02-21 | 山东理工大学 | Rigid-variable torsional vibration reducer of clutch of automobile |
| WO2008106926A1 (en) * | 2007-03-08 | 2008-09-12 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torsional vibration damper |
| DE102008018218A1 (en) * | 2007-05-07 | 2008-11-13 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Divided flywheel, for an internal combustion motor, has a secondary inertia mass with springs and a primary limit working with an overload safety unit |
| DE102013221655A1 (en) * | 2013-10-24 | 2015-04-30 | Schaeffler Technologies Gmbh & Co. Kg | torsional vibration dampers |
-
2015
- 2015-02-20 DE DE102015203105.5A patent/DE102015203105B4/en active Active
-
2016
- 2016-02-12 EP EP16708350.0A patent/EP3259490A1/en not_active Withdrawn
- 2016-02-12 DE DE112016000810.4T patent/DE112016000810A5/en not_active Withdrawn
- 2016-02-12 CN CN201680008419.9A patent/CN107208735B/en active Active
- 2016-02-12 WO PCT/DE2016/200093 patent/WO2016131457A1/en active Application Filing
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1272601A (en) * | 1999-02-26 | 2000-11-08 | 易通公司 | Friction clutch with predamper |
| GB2413615A (en) * | 2004-05-01 | 2005-11-02 | Safe Developments Ltd | A clutch friction plate assembly |
| FR2918141A1 (en) * | 2007-06-26 | 2009-01-02 | Valeo Embrayages | TORSION OSCILLATION DAMPING DEVICE, IN PARTICULAR FOR A FRICTION CLUTCH, FOR EXAMPLE FOR A MOTOR VEHICLE. |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2016131457A1 (en) | 2016-08-25 |
| DE102015203105A1 (en) | 2016-08-25 |
| EP3259490A1 (en) | 2017-12-27 |
| DE102015203105B4 (en) | 2017-12-14 |
| DE112016000810A5 (en) | 2017-11-16 |
| CN107208735A (en) | 2017-09-26 |
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