CN107208735A - Torsional vibration damper - Google Patents
Torsional vibration damper Download PDFInfo
- Publication number
- CN107208735A CN107208735A CN201680008419.9A CN201680008419A CN107208735A CN 107208735 A CN107208735 A CN 107208735A CN 201680008419 A CN201680008419 A CN 201680008419A CN 107208735 A CN107208735 A CN 107208735A
- Authority
- CN
- China
- Prior art keywords
- output
- stop part
- flange
- input component
- torsional vibration
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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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
Abstract
Torsional vibration damper (100), especially double mass flywheel, with input component (102) and output (104) with common rotation axis (106), input component (102) and the output (104) can surround the pivot center common rotation and can limitedly reverse relative to each other, and, the torsional vibration damper has what is worked between the input component (102) and the output (104), spring cushion device with least one accumulator (108), and the torsional vibration damper has secondary stop device, wherein, the input component (102) and the output (104) have corresponding secondary stop part (118 respectively, 120, 124, 126), in the torsional vibration damper, the secondary stop part (118 of the input component (102), 120) and/or the output (104) secondary stop part (124, 126) it is made up of 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 has：With common
The input component and output of pivot center, the input component and output can together be rotated and energy around the pivot center
It is enough limitedly to reverse relative to each other；The spring cushion device worked between input component and output, the spring damping
Device has at least one accumulator；And secondary stop device, wherein, input component and output have corresponding secondary respectively
Stop part.
Background technology
From a kind of flanged component known to the A1 of DE 195 22 718, for being loaded with 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 extended in radial directions of the component is respectively disposed between mutual end, wherein, the arm is (in the axial direction
On see) be for example arranged on housing 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 at least one arm has the shape different from other arm for another loading direction, with
Just the transition produced in the case where being transitioned into coast region by elasticity and vibration damping resistance is rigidly reduced to as low as possible
Level on, and spring is kept underload under stress conditions herein, the stress is compacted by the spring
(auf Block) is produced.
It is with driving side and slave end from a kind of torsional vibration damper known to the A1 of DE 10 2,008 009 656
Transmitting element, the transmitting element can be reversed relative to each other against at least one set between them vibration absorber,
The vibration absorber has at least one long helix spring worked in the circumferential, wherein, transmitting element, which has, is used for spiral
The loading area of spring and helical spring inner radial is provided with 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 worked between two transmitting elements (to be especially made up of helical spring
Accumulator) with antioverloading.
From a kind of torsional vibration damper, especially divided flywheel known to the 218A1 of DE 10 2,008 018, with first
Level flywheel mass and secondary flywheel mass, the primary flywheel mass can be connected with the drive shaft anti-torsion of internal combustion engine, institute
The resistance at least two energy storage devices that secondary flywheel mass resistance is worked in circumferential direction is stated in lead and inertia
It can be reversed on line of travel relative to primary flywheel mass, the primary flywheel mass has stops for the primary of energy storage device
Blocking means, wherein, the primary stop device for energy storage device is included in the overload protection arrangement worked 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.
The content of the invention
The present invention is based on following tasks：In structure and/or functionally improve the torsional vibration damper that introductory song is previously mentioned.Especially
Accumulator is avoided to fail.Especially arc spring is avoided to fail.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 is damaged and stopped (Liegenbleiben).Especially to prevent drivetrain from interrupting.Especially to optimize secondary stop part
Adaptation hit configuration.Especially to reduce due to load caused by impact.
The solution of the task realizes that it has by a kind of torsional vibration damper, especially double mass flywheel：With common
The input component and output of pivot center, the input component and output can together be rotated and energy around the pivot center
It is enough limitedly to reverse relative to each other；The spring cushion device worked between input component and output, the spring damping
Device device has at least one accumulator；And secondary stop device, wherein, input component and output have corresponding time respectively
Level 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
Individual additional flange is constituted.
Because the secondary stop part of input component and/or the secondary stop part of output are made up of at least one additional flange,
The rigidity of secondary stop part can be influenceed in structure in other regions, so as to can avoid in the case of an overload or at least
Minimize the damage of component.The secondary stop part of output can be made up of additional flange.The secondary stop part of output can be with
It is made up of the additional flange of multi-piece type.The secondary stop part of output can be made up of the additional flange of two-piece type.Input component
Secondary stop part can be made up of additional flange.The secondary stop part of input component can be made up of the additional flange of multi-piece type.It is defeated
Entering the secondary stop part of part can be made up of the additional flange of two-piece type.
The torsional vibration damper can be used for being arranged in the drivetrain of motor vehicle.The drivetrain can have internal combustion engine.Should
Drivetrain can have friction clutch device.Friction clutch device can have double clutch.Drivetrain, which can have, to be become
Fast device.Speed changer can be dual-clutch transmission.Drivetrain can have the wheel that at least one can drive.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 that the periodic process by periodic process, especially in internal combustion engine is excited.Turn round
The shock absorber that shakes can work on coast direction and/or in lead.Coast direction is sensing 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 connected in input component side with bent axle.Belt pulley decoupling device can be with
It is connected in output side with belt pulley, the belt pulley for example drives auxiliary unit.
Input component and output can be supported by means of bearing in the way of it can mutually reverse.Input component can be used for driving
Move the connection of side, be especially connected 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
Individual spring can be helical spring.At least one spring can be arc spring.At least one accumulator can be in coast
Worked on direction and/or in lead.At least one accumulator can be acted as on pivot center with an operating radius
With.
At least one accumulator can be high power capacity spring.High power capacity spring is optimised in terms of possible shock.Only
Super torque in the case of gear formula load is it will be appreciated that to hit, this occurs for example when vehicle stops in double mass flywheel.
Because being difficult to avoid hitting completely, it is necessary to which the fastness increased by torsional vibration damper stops shock.Therefore, high power capacity spring can
To make significant contribution.
At least one accumulator can be the arc spring of the spiral spacing with increase.At least one accumulator can be
High power capacity arc spring.High power capacity arc spring has the spiral spacing of increase.It is possible thereby to significantly increase stopping for arc spring
Keep off torque.High power capacity arc spring can store about many 30% compared with conventional arc spring in the case where not occurring backstop
To 50% energy.The wire thickness of high power 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 keep constant.The specified spring rate of high power capacity spring can be than conventional arc spring
Specified spring rate somewhat higher.High power capacity arc spring helps avoid arc spring deformation.Double mass flywheel is by height
Capacity arc spring significantly becomes firm and durable, without reducing traction isolation performance (Zugisolation).
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.The anchor ring formula that flange section and cover region section can be used at least one the first accumulator with gauge connects
Receive space.
Output can have flange part.Additional flange can be connected with the flange part.Output can have flywheel matter
Measure part.Additional flange can be arranged between the flange part and the flywheel mass part in the axial direction.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 the flange section of input component and cover region section between.Additional flange and cover region section can be with cloth
Put on identical axial location.Flywheel mass part can be arranged in the axial direction cover region section on the side of flange section.
" in the axial direction " and " diametrically " 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
Level 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
At least one described accumulator of support.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 radially outer in reception space.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
Individual 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, is left 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 more than 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.The secondary stop part of input component side and output
The secondary stop part of part side abuts that can also be considered as secondary stop part works.When reaching the torsion angle of maximum,
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 avoided the damage of accumulator.In addition,
Sliding block can be clipped on 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
Footpath.Secondary stop part can be respectively diametrically mutually opposing.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 opposing.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 up of additional flange.Additional flange can be by least two flange section groups
Into.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 up 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 be surrounded
The pivot center of torsional vibration damper is constructed deviously.Flange section can have the through hole for being used for riveting with output.Flange section can
With with through hole being riveted for the flange part with output and flywheel mass part, in the base.Matrix is in circumferential direction
There can be two end regions, in the end regions, it constriction and is 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 with extension in general radial direction.Flange
Section can have lucky two backstop wings.
Additional flange can have lucky two flange sections, and the flange section has lucky two flange wings respectively.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
With 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 put and base
Body is connected.The first flange wing and the second flange wing can be speculars.Two first of two flange sections of additional flange
The backstop wing can be disposed adjacent in circumferential direction.Two first backstop wings of two flange sections may be constructed time of output
Level stop part.Two second backstop wings of two flange sections can be disposed adjacent in circumferential direction.The two of two flange sections
The individual second backstop wing may be constructed the secondary stop part of output.Because each in two secondary stop parts is by two backstop wings
Constitute, secondary stop part has the rigidity smaller than the secondary stop part of single type of identical size respectively.Thus, additional flange
Secondary stop part can avoid or at least minimize the component damage in drivetrain in the event of overloading.The end of the backstop wing
Portion can deviate from pivot center.The backstop wing can be arranged in the secondary stop part identical plane with input component.Additional flange
The path of the backstop wing can be overlapping with the path of the secondary stop part of input component in radial directions so that in input component and defeated
Go out between part and be merely capable of limitedly relatively rotating.
At least one in secondary stop part can be constituted so flexiblely so that be avoided in the case of an overload or minimum
The damage of change component, the damage of the component especially in the drivetrain of torsional vibration damper is disposed with.The secondary backstop of output side
Part can be with the flexible backstop wing.The flange section of additional flange can be with the flexible backstop 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 power 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 fixing points), the flange of fixed, two-piece type is matched somebody with somebody
Close in leaving a blank in the lid.The two-piece type geometry and the elastic bolster guide wing of additional flange to produce it is as soft as possible only
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 so cast by corresponding configuration so that against when also allow system determination residue rigidity.By
This remaining component of protection in drivetrain is with antioverloading.
The present invention may be mounted in double mass flywheel and shock absorber and in belt pulley decoupling device.By so
Mode avoid arc spring from failing：Stop part protects arc spring to prevent its excess load, especially because caused by compaction state
Excess load.High power capacity spring is preferably installed.In addition, realizing following torsional rigids, the torsion by the suitable configuration of component
Turn the damage that rigidity minimizes the component in drivetrain in the case of an overload.
Torsional vibration damper can have centrifugal pendulum mechanism.Centrifugal force pendulum can be used for improving effect of 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 flange section and the 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 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 the way of it can shift
Put.At least one described pendulum mass can be displaced in run location under the action of the centrifugal force.In run location, 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 centre position
Swing 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 can also be arranged on lid
On disk or on support sheet material.
By the especially optional feature of " can with " description present invention.Therefore, following implementations of the present invention are respectively present
Example, the embodiment has one or some corresponding features.
By avoiding accumulator from failing according to the torsional vibration damper of 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 because torsional vibration damper is damaged and is stopped.Especially prevent drivetrain from interrupting.Especially optimization secondary is stopped
The configuration that the adaptation of block piece is hit.Especially reduce due to load caused by impact.
Brief description of the drawings
Embodiments of the invention are explained referring to the drawings.Other feature and advantage are drawn from the explanation.Should
The specific features of embodiment can show the general characteristic of the present invention.The embodiment also may be used with the feature that further feature is combined
To show each feature of the present invention.
It schematically and is exemplarily illustrated：
Fig. 1 shows the part week of torsional vibration damper in the state of 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 dampers.
Embodiment
Fig. 1 shows torsional vibration damper 100.The torsional vibration damper 100 is used herein to be arranged in the drivetrain of motor vehicle
Between internal combustion engine and friction clutch device, such as double mass flywheel or double clutch shock absorber.Torsional vibration damper 100
With input component 102 and output 104.Torsional vibration damper 100 has pivot center 106, input component 102 and the energy of output 104
Enough rotate and can be limitedly reversed relative to each other together around the pivot center.Input component 102 and output 104 it
Between, arc spring 108 works as accumulator.Here, torsional vibration damper 100 has the arc bullet of two substantially semicircle arcuations
Spring 108.The arc spring 108 is embodied as high power capacity spring and with the spiral spacing of increase.In input component 102 and output
In the case that part 104 is reversed relative to each other, the storage energy of arc spring 108 releases energy in other words.In addition, rubbing device is defeated
Enter and worked 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 is excited.
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 cover region 112 gauges of 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 on flange section 110 and cover region section opposed to each other in the axial direction
On 112.Here, cover region section 112 has two primary stop parts 114,116.Primary stop part 114,116 is diametrically mutually right
Arrange with putting.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 is 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 on cover region
In section 112.Here, cover region section 112 has two secondary stop parts 118,120.Secondary stop part 118,120 is diametrically mutual
It is opposed to arrangement.Secondary stop part 118,120 cover region section 112 circumferential direction on be centrally disposed in primary stop part 114,
Between 116.Here, secondary stop part 118,120 is arranged with staggering 90 ° relative to primary stop part 114,116.Cover region section 112
With leaving a blank for largely circle.It is described leave a blank it is round-shaped by secondary stop part 118,120 interrupt.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 footpath
Extended up to side in described leave a blank.Secondary stop part 118,120 is implemented with cover region section 112 into a ground.Secondary stop part
118th, 120 diametrically more internally arranged than the operating radius of arc spring 108.In circumferential direction, two secondary backstop
It is each by two stop surface gauges in part 118,120.
Output 104 has flange part 122 and in the accompanying drawings unshowned flywheel mass part.Flange part 122 has to footpath
The flange wing being extend into outside in reception space.The flange wing is used in the collateral support arc of output as primary stop part
Spring 108.Flange part 122 and flywheel mass part are mutually riveted in the case of being provided with additional flange 128 in-between.
Here, output 104 has the additional flange 128 with two secondary stop parts 124,126.Therefore, output
104 secondary stop part 124,126 is made up of additional flange 128.Additional flange 128 is arranged in flange part in the axial direction
Riveted between 122 and flywheel mass part and with it.Additional flange 128 is made up of two flange sections 130,132.Fig. 2 shows to make
For the flange section 130 of single-piece.The minute surface that the two flange sections 130,132 are arranged therein on pivot center 106 is mirror image pair
Claim.Each flange section 130,132 is made up of the backstop wing 138,140 of matrix 134,136, first and the second backstop wing 142,144.
Each first matrix 134,136 is flat and constructed deviously around pivot center 106.Each two in matrix 134,146
Individual through hole is used to rivet with flange part 122 and flywheel mass part.In circumferential direction, each matrix 134,136 has two ends
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 adjacent to and constitute output 104 in circumferential direction
Another secondary stop part 126.Thus, in described two secondary stop parts 124,126 it is each by two backstop wings 138,
140th, 142,144 constitute, secondary stop part 124,126 has the intensity smaller than the secondary stop part of single type of identical size.
Thus, secondary stop part 124,126 can avoid or at least minimize the damage of the component in drivetrain in the case of an overload
It is bad.Secondary stop part 124,126 is diametrically more internally arranged than the operating radius of arc spring 108.Secondary stop part
124th, 126 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 is arranged in same level with the secondary stop part 118,120 of input component 102.Radially
On direction, the path of the backstop wing 138,140,142,144 of the secondary stop part 124,126 of output 104 and input component 102
The path of secondary stop part 118,120 is overlapping, so as to be merely capable of between input component 102 and output 104 limitedly relative
Rotate.
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 are reversed 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 do not come in contact.More than maximum internal combustion
During machine power square, input component 102 and output 104 are reversed until following degree relative to each other：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 come in contact.Then,
In the case where arc spring 108 is not switched on therebetween, directly machinery is carried out between input component 102 and output 104
Power is transmitted, and torsional vibration damper 100 is rigidly attached, and arc spring 108 is not compacted.Thus, arc spring 108 is less
Intensity ground load, and firmly (impact resistance) design in terms of shock of torsional vibration damper 100.
Reference numerals list
100 torsional vibration dampers
102 input components
104 outputs
106 pivot centers
108 accumulators, arc spring
110 flange sections
112 cover regions section
114 primary stop part input component sides
116 primary stop part input component sides
118 level stop part input component sides
120 level stop part input component sides
122 flange parts
124 level stop part output sides
126 level 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 (10)
1. torsional vibration damper (100), especially double mass flywheel, the torsional vibration damper have：With common rotation axis
(106) input component (102) and output (104), the input component (102) and the output (104) can be around described
Pivot center is rotated and can limitedly reversed relative to each other together；In the input component (102) and the output (104)
Between the spring cushion device that works, the spring damper has at least one accumulator (108)；And secondary is stopped
Blocking means, wherein, the input component (102) and the output (104) have respectively corresponding secondary stop part (118,120,
124th, 126), it is characterised in that the secondary stop part (118,120) of the input component (102) and/or the output
(104) the secondary stop part (124,126) is made up of at least one additional flange (128).
2. torsional vibration damper (100) according to claim 1, it is characterised in that the additional flange (128) is by least two
Individual flange section (130,132) composition.
3. according to described torsional vibration damper (100) at least one of in above claim, it is characterised in that it is described at least one
Accumulator (108) is high power capacity spring.
4. according to described torsional vibration damper (100) at least one of in above claim, it is characterised in that it is described at least one
Accumulator (108) is the arc spring of the spiral spacing with increase.
5. the torsional vibration damper (100) according at least one in above claim, it is characterised in that in the accumulator
(108) in the case of pretension, the input component (102) can be reversed in so far relative to the output (104)：Until
The secondary stop part (118,120) of the input component (102) and the secondary stop part of the output (104)
(124,126) contact with each other, and the accumulator (108) is not clamped to compaction state.
6. the torsional vibration damper (100) according at least one in above claim, it is characterised in that time of output side
At least one in level stop part (124,126) is particular by so soft in the flexible backstop wing (138,140,142,144)
Tough ground configuration so that avoid or minimize in the case of an overload the damage of component, the component is especially being disposed with the torsion
In the drivetrain of shock absorber (100) of shaking.
7. the torsional vibration damper (100) according at least one in above claim, it is characterised in that the input component
(102) there is flange section (110) and cover region section (112), also, input component side is configured with cover region section (112)
Secondary stop part (118,120).
8. torsional vibration damper (100) according to claim 7, it is characterised 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 extend into described in leaving a blank, and the secondary backstop of the output side
Part (124,126) is arranged in described in leaving a blank.
9. the torsional vibration damper (100) according at least one in above claim, it is characterised in that the output
(104) there is flange part (122), and the additional flange (128) is connected with the flange part (122).
10. the torsional vibration damper (100) according at least one in above claim, it is characterised in that the output
(104) there is flange part (122) and flywheel mass part, also, the additional flange (128) is arranged in the flange in the axial direction
Between part (122) and the flywheel mass part.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102015203105.5A DE102015203105B4 (en) | 2015-02-20 | 2015-02-20 | torsional vibration dampers |
| DE102015203105.5 | 2015-02-20 | ||
| PCT/DE2016/200093 WO2016131457A1 (en) | 2015-02-20 | 2016-02-12 | Torsional vibration damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107208735A true CN107208735A (en) | 2017-09-26 |
| CN107208735B 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) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111919047A (en) * | 2018-04-10 | 2020-11-10 | 舍弗勒技术股份两合公司 | Torsional vibration damper |
| CN114341523A (en) * | 2019-09-02 | 2022-04-12 | 舍弗勒技术股份两合公司 | Torsional vibration damper with centrifugal pendulum and predamper |
Families Citing this family (8)
| 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 |
| FR3069602B1 (en) * | 2017-07-28 | 2020-08-28 | Valeo Embrayages | SHOCK ABSORBER WITH ELASTIC LIMIT STOP |
| FR3069603B1 (en) * | 2017-07-28 | 2019-08-23 | Valeo Embrayages | TORSION SHOCK ABSORBER WITH ELASTIC END LIMIT STOP |
| WO2019020808A2 (en) * | 2017-07-28 | 2019-01-31 | Valeo Embrayages | Torsional vibration damper with elastic end-stop |
| FR3069600B1 (en) * | 2017-07-28 | 2020-07-03 | Valeo Embrayages | TORSION SHOCK ABSORBER WITH ELASTIC LIMIT 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 |
| 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 |
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| CN1272601A (en) * | 1999-02-26 | 2000-11-08 | 易通公司 | Friction clutch with predamper |
| US20020019263A1 (en) * | 2000-07-27 | 2002-02-14 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Apparatus for damping torsional vibrations in the power trains of motor vehicles and the like |
| GB2413615A (en) * | 2004-05-01 | 2005-11-02 | Safe Developments Ltd | A clutch friction plate assembly |
| CN2871973Y (en) * | 2006-03-06 | 2007-02-21 | 山东理工大学 | Rigid-variable torsional vibration reducer of clutch of automobile |
| 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. |
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| 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 |
| 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 WO PCT/DE2016/200093 patent/WO2016131457A1/en active Application Filing
- 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
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1272601A (en) * | 1999-02-26 | 2000-11-08 | 易通公司 | Friction clutch with predamper |
| US20020019263A1 (en) * | 2000-07-27 | 2002-02-14 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Apparatus for damping torsional vibrations in the power trains of motor vehicles and the like |
| GB2413615A (en) * | 2004-05-01 | 2005-11-02 | Safe Developments Ltd | A clutch friction plate assembly |
| CN2871973Y (en) * | 2006-03-06 | 2007-02-21 | 山东理工大学 | Rigid-variable torsional vibration reducer of clutch of automobile |
| 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. |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111919047A (en) * | 2018-04-10 | 2020-11-10 | 舍弗勒技术股份两合公司 | Torsional vibration damper |
| US11378154B2 (en) | 2018-04-10 | 2022-07-05 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper |
| CN114341523A (en) * | 2019-09-02 | 2022-04-12 | 舍弗勒技术股份两合公司 | Torsional vibration damper with centrifugal pendulum and predamper |
| CN114341523B (en) * | 2019-09-02 | 2024-03-05 | 舍弗勒技术股份两合公司 | Torsional vibration damper with centrifugal pendulum and pre-damper |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102015203105B4 (en) | 2017-12-14 |
| DE112016000810A5 (en) | 2017-11-16 |
| DE102015203105A1 (en) | 2016-08-25 |
| CN107208735B (en) | 2019-11-15 |
| WO2016131457A1 (en) | 2016-08-25 |
| EP3259490A1 (en) | 2017-12-27 |
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