CN109210133A - Torsional vibration damper - Google Patents
Torsional vibration damper Download PDFInfo
- Publication number
- CN109210133A CN109210133A CN201810558215.3A CN201810558215A CN109210133A CN 109210133 A CN109210133 A CN 109210133A CN 201810558215 A CN201810558215 A CN 201810558215A CN 109210133 A CN109210133 A CN 109210133A
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- Prior art keywords
- spring
- reset
- torsional vibration
- vibration damper
- damper
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- 230000008878 coupling Effects 0.000 claims description 18
- 238000010168 coupling process Methods 0.000 claims description 18
- 238000005859 coupling reaction Methods 0.000 claims description 18
- 230000000694 effects Effects 0.000 claims description 7
- 230000003044 adaptive effect Effects 0.000 description 6
- 238000013016 damping Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 101150042248 Mgmt gene Proteins 0.000 description 2
- 238000005119 centrifugation Methods 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
- 238000000034 method Methods 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000008901 benefit Effects 0.000 description 1
- 244000309464 bull Species 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000001965 increasing effect Effects 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/14—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
- F16F15/1414—Masses driven by elastic elements
- F16F15/1421—Metallic springs, e.g. coil or spiral springs
- F16F15/1428—Metallic springs, e.g. coil or spiral springs with a single mass
-
- 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
- F16F15/123—Wound springs
-
- 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
- F16F15/1202—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 the damping action being at least partially controlled by centrifugal masses
-
- 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
- F16F15/123—Wound springs
- F16F15/12306—Radially mounted springs
-
- 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
- F16F15/123—Wound springs
- F16F15/1232—Wound springs characterised by the spring mounting
-
- 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
- F16F15/1414—Masses driven by elastic elements
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The invention relates to a torsional vibration damper comprising a drive part (2) which can be rotated about a rotational axis and a damper mass part (4) which can be rotated about the rotational axis relative to the drive part (2), wherein the damper mass part (4) can be reset from a position deflected relative to the drive part (2) by means of a reset force which is generated by at least one spring element (6) which compresses in rotation and at least one reset device (9) which acts as a function of centrifugal force.
Description
Technical field
The present invention relates to a kind of torsional vibration dampers comprising can around pivot axis driving part and can around turn
The damper quality part that shaft line is rotated relative to driving part.
Background technique
This torsional vibration damper, which is used, is carrying out vibration damping or damping, transfer of torque device to possible twisting vibration
In, it is so-called spring mass-damper.For example, this torsional vibration damper is arranged in the powertrain of motor vehicle,
Vibration damping is carried out to be inherently input to the twisting vibration in powertrain from internal combustion engine to usual system.
This torsional vibration damper is usually by can surrounding pivot axis and load the driving part of torque and opposite
It can be constituted around the damper quality part of pivot axis in driving part, wherein driving part and damper quality part
Spring can be usually overcome relative to each other to act on and rotate via one or more spring elements.Due to the moment of inertia, damper quality
Component overcomes the effect of one or more spring elements to shift when inputting twisting vibration via driving part, so that via spring
Deformation and relative motion extracting energy from vibration, and time delay be conveyed to system again.Via the damper energy
Enough realize keeps change in torque steady, so that torque obtained, speed changer that be for example output to downstream connection is more evenly.This
The example of kind torsional vibration damper illustrates in 10 2,014 223 308 A1 of DE 198 40 664 A1 or DE.
As being described in detail, driving part overcomes one or more bullets relative to the relative torsion of damper quality part
Spring element carries out, and the spring element deforms herein.Because the corresponding frequency and amplitude of vibration are become based on deflecting
The torque of change works, and the torque causes to deflect, therefore the torque increaseds or decreases.Thus it is desirable that: driving part
Deflection relative to damper quality part also resets again as quickly as possible.Only exist via one or more here, resetting
The spring element compressed when deflection carries out.However, the reseting torque or the reset force can once in a while on rare occasion not
It is always sufficient so as to be resetted in the desired manner.
Summary of the invention
Therefore, the purpose that the present invention is based on is: proposing relative to this improved torsional vibration damper.
In order to realize the purpose, it in the torsional vibration damper for starting to propose type, proposes according to the present invention: damper matter
Amount component can be resetted via reset force from the position deflected relative to driving part, and the reset force is being turned round by least one
The spring element compressed when turning and at least one resetting apparatus generation acted on according to centrifugal force.
In torsional vibration damper according to the present invention, especially advantageously be equipped with combined reset, it is described reset by one or
The reset force that the reset force and revolving speed of multiple spring elements compressed in deflection are adaptive is formed, and the revolving speed is adaptive to answer
Position power is generated by the resetting apparatus acted on according to centrifugal force.In torsional vibration damper according to the present invention, in damper quality
One or more spring elements are equipped between component, such as quality loop and driving part, the spring element is pressed in deflection
It contracts and generates the first reset force share.Additionally, it is worked according to the resetting apparatus of centrifugal force effect, the resetting apparatus will be attached
The adaptive reset force of the revolving speed added or the adaptive reseting torque of revolving speed are applied on damper quality part.Therefore, cause
Two combinations or addition for resetting force component or reseting torque generated via individual mechanism, the reset force component or reset
Torque jointly acts on damper quality part.
The reset of the combination advantageously causes the raising of reseting torque, wherein the reseting torque is bigger, revolving speed or centrifugation
Power is bigger, and the revolving speed or centrifugal force act on the resetting apparatus according to centrifugal force effect.
Thus the significantly improved reset that can be realized the deflection of damper quality part, also causes damper performance
It improves.
Here, the damper quality part can be coupled via at least one along the spring element of ring circumferential direction effect,
And the reset element that there is resetting apparatus at least one can be moved radially according to centrifugal force, the reset element and damper quality
Component couples.Spring that is that first reset component is acted on via one or more along ring circumferential direction and then also being compressed along ring circumferential direction
Element provides, therefore the spring element is compressed along torsional direction.The feature for providing the resetting apparatus of the second reset component exists
In: the reset element that can be moved radially according to centrifugal force, the reset element is along the centrifugal force or centrifugation for being deflected or being moved
The direction of active force is mobile, so as to sensitively generate reset force to revolving speed.
Here, can pivotally support reset element, therefore it is necessarily configured to a kind of lever and pivotally supports
On the driving part.As an alternative, there is also following feasibilities: being moved linearly by reset element, in this case certain preferred diameter
It is mobile to ground.It is pivotable now with reset element or can supports to linear movement unrelated, it is advantageous that via coupling element
It is coupled with damper quality part.
Be also advantageous in that: reset element is radially outward tensioned via at least one spring member, this is to say, via spring
Preload is applied in reset element by component, it is described pre-tighten by the reset element via coupling element for good and all with damper matter
Amount component couples.This spring member is, for example, simple spiral compression spring.
As being described in detail, reset element is coupled to damper quality via coupling element.The coupling element root
Form, which is advantageously improved, according to of the invention one is configured to roller.In order to guide the roller, at this in reset element and/or
The guide rail to arch upward is equipped on damper quality part, roller rolls on the guide rail.Via guide rail
Geometry correspondingly can limit or set the reset force along the effect of ring circumferential direction in conjunction with the power being applied on coupling element.
As described, there are following feasibilities: bearing is pivoted to reset element, it is in this case, described
Reset element is configured to the hinged pivot rods in side, and the pivot rods are radially outward pre-tightened preferably via spring member.As an alternative,
In the case where reset element linear movement bearing, the reset element is configured to mobile piston, this is to say, linear for energy
Mobile moving member, for example constituting on the moving member has guide rail, and accommodating on the guide rail is in roller form
Coupling element.
The embodiment that alternative is described in the upper surface of resetting apparatus, wherein the resetting apparatus includes the pivotable of rod type
The linearly displaceable reset element of the reset element of bearing or mobile movement, wherein the reset element is respectively via rolling
The coupling element of the forms such as son is coupled with damper quality part, and the second variations of the invention propose: resetting apparatus is setting
Leg spring on the driving part, the leg spring is coupled with damper quality part via coupling roller, described to couple roller
It is rolled on the raceway of leg spring.In the invention variations, therefore leg spring is used, the leg spring is via coupling roller
It is coupled with damper quality part.The roller that couples rolls on the raceway of leg spring to arch upward, so that according to roller is coupled
Relative position on guide rail obtains the deformation of leg spring, and the deformation is used for vibration damping.On the other hand, leg spring or its leg
Portion is also according to centrifugal force radial deformation, this is to say, forms reset force via roller deformation is coupled via leg spring one side,
But then also due to the adaptive radial deflection of revolving speed and form additional reset component, wherein coupling roller in the leg
It is moved in portion.Now, other than following reset forces, this also works according to the reset force component of revolving speed, the reset force warp
Applied by one or other spring element, usual helical spring, wherein the spring element is preferably arranged along ring circumferential direction again
Or effect, and couple driving part and damper quality part via the spring element.In this design scheme, because
This, using helical spring or one or more spring elements of at least one leg spring form, the spring element respectively with drive
It dynamic component and is coupled with damper quality part.Here, the reset response of one or more spring elements of leg spring form
And the entire resetting movement for resetting component and supporting damper quality part of leg spring, the reset component also have centrifugal force
The reset component determined.
As already described, it is advantageous that the spring element or each spring element, such as it is described helically
The spring element of form of springs is supported on damper Quality Mgmt Dept on the driving part and with the other end with an end support
On part.In this regard, being equipped with the receiving portion or support corresponding to both parts for helical spring.
Of the invention one is advantageously improved form proposition: equipped with other spring member, the spring member is by frame leg
The section with raceway of spring is radially outward tensioned.The spring member, such as be again helical spring, setting in driving part and
It between the leg of leg spring and is supported in the two, couples roller and moved on the leg.Via the spring element,
Leg radially outward pre-tightens, therefore necessarily by coupling element relative to carrying quality part tensioning.Through thereby, it is possible to further
Improve reset response in ground.
Advantageously about two invention alternatives: multiple spring elements, the helical spring especially having been described surround
Ring week is arranged in a distributed manner.Here, the spring element is on identical radius or on different radiuses.The spring
Element can also be located in common plane or axially be arranged with offseting one from another.Similarly, it can be considered that: additionally or alternatively
It also is provided with multiple resetting apparatuses around the distributed setting of ring week.Therefore, in the case where the first alternative, multiple pivots are equipped with
Bull stick, such as two be offset from one another 180 ° of opposite pivot rods, or move piston accordingly.Also it can be considered that: for example
If the leg spring is bonded on common driving part there are two 180 ° of opposite leg springs are equally offset from one another.
Detailed description of the invention
In the following, the present invention is described with reference to the drawings according to embodiment.Attached drawing is schematical diagram and shows:
Fig. 1 shows the schematic diagram of the part figure form of the first embodiment of torsional vibration damper according to the present invention,
Fig. 2 shows the sectional view along the line II-II in Fig. 1,
Fig. 3 shows the sectional view along the line III-III in Fig. 1,
Fig. 4 shows the sectional view along the line IV-IV in Fig. 1,
Fig. 5 shows the schematic diagram of the second embodiment of torsional vibration damper according to the present invention,
Fig. 6 shows the schematic diagram of the third embodiment of torsional vibration damper according to the present invention, and
Fig. 7 shows the part figure of the torsional vibration damper in Fig. 6 with additional spring member.
Specific embodiment
Fig. 1 shows the schematic diagram of torsional vibration damper 1 according to the present invention comprising driving part 2, the driving part energy
Enough via interior teeth portion 3 and axis connection.It is additionally provided with the damper quality part 4 of 5 form of quality loop, the damper quality part can
Central axial line or pivot axis are surrounded relative to driving part 2.Driving part 2 and damper quality part 4 can be via
It is preferred that helically multiple spring elements 6 of the form of spring 7 overcome its reset force to reverse, i.e., helical spring 7 is mutually turned round in component
It is compressed when turning, reset force is consequently formed, when the torque for reversing the component reduces again, the reset force is by the two portions
Part resets to initial position again.
It is contained in corresponding recess portion 8 symmetric around the spring element 6 of ring week distribution and is supported there in end side,
So that two components all cause the compression of spring element 6, the recess portion along any relative torsion of two torsional directions to each other
Be formed on driving part 2 and damper quality part 4 on.
In addition, being equipped with additional resetting apparatus 9, the resetting apparatus is used for: supporting the reset of the component 2,4 of two rotations
Process.The resetting apparatus 9 includes the reset element 10 of 11 form of pivot rods, and the pivot rods can be rotated around pivot axis 12
Ground is fixed on driving part 2.The pivot rods have arcuate shape at least on its radial outside 13, in the radial outside
Upper composition has arc or waveform concave portion 14.The female portion 14 is opposite with same arc or waveform concave portion 15
It sets, the female portion 15 is formed in the inner circumference of damper quality part 4, i.e. quality loop 5.The coupling of 17 form of ball or roller
Connection element 16 is contained in two concave portions 14,15 between pivot rods 11 and quality loop 5, and the ball or roller can be moved freely
Dynamic ground rolls on guide rail 18,19, and the guide rail is constituted via concave portion or the structure in the region of concave portion 14,15
At.Ball or roller 17 are also retained between two unshowned quality parts.
The function of resetting apparatus 9 depends on centrifugal force, and this is to say, reset force is depending on centrifugal force, and therefore
Depending on revolving speed, revolving speed or centrifugal force are bigger, and reset force is bigger, wherein the reset force is by two torsions relative to each other
Part 2,4 is reset in initial position again.This is to say, due to centrifugal force, pivot rods 11 are radially outward squeezed.Here, institute
State pivot rods by roller 17 be pressed against quality loop, the roller due to driving part 2 relative to carrying quality part 4 torsion and
It is moved on the guide rail 18,19 of rising.Therefore, by variable radial force, in conjunction with the gradient of guide rail 18,19, via
The resetting apparatus 9 generates variable, according to centrifugal force reset force, wherein the variable radial force passes through pivot rods 11
It deflects and is applied on roller 17 caused by centrifugal force, wherein the reset force has the component oriented along ring circumferential direction.
This additionally acts on the spring element 6 via deformation, i.e. spiral via the reset force component that resetting apparatus 9 generates
The reset that spring 7 carries out.Therefore, two reset force shares are summed into total reset force, and total reset force is noticeably greater than only
The reset force generated via spring element 6.Therefore, it significantly can faster and more effectively be resetted.
In addition, another advantage of described design scheme is other than improving and resetting and then improve damper performance
The backstop noise for avoiding 11 aspect of pivot rods on damper quality part 4, because this is prevented via spring element 6.
By the embodiment of the spring element 6 with nonlinear characteristic curve, it also can be realized and obtained via spring element 6
The raising of the reset force component obtained, wherein the raising depends on deflection.
Optionally, because non-mandatorily, it is also shown that additional spring member 20, only dotted line shows the spring member herein
Out.The spring member side be supported at driving part 2 equally only on the support 21 shown in dotted line, and in the other side
It is supported on the inside of pivot rods 11.Via the spring member 20, reset element 10 is radially outward pre-tightened, herein i.e. pivot rods
11, so that the pivot rods are permanently coupled with roller 17 and then with quality loop 5.
Fig. 2 to 4 shows the different cross-sectional views in different sections.Fig. 2 shows the cross-sectional views along line II-II.Driving is shown
Component 2, the driving part is by internal, the hub component 22 of sleeve shaped and 23 structure of load-bearing part for the dish type being fixed thereon
At.Pivot rods 11 are fixed on load-bearing part 23, fulcrum post 24 (referring to Fig. 3) are used to this, the fulcrum post is formed simultaneously pivot
Axis 12.
Roller 17 and quality loop 5 are also shown other than pivot rods 11 and is arranged on pivot rods 11 and is arranged by Fig. 2
Guide rail 18,19 on quality loop 5.
As described, Fig. 3 shows the cross-sectional view of the supporting portion through pivot rods 11, and Fig. 4 is shown through spring element
The cross-sectional view in the region of part 6, the spring element are configured to helical spring 7.Also significantly it is seen that recess portion 8, helical spring 7 hold
It is contained in the recess portion.
Fig. 5 shows another design side according to the present invention of the torsional vibration damper according to the present invention 1 of second embodiment
Case, wherein using identical appended drawing reference for identical component.
It also is provided with the damper quality part 4 of 5 form of driving part 2 and quality loop herein, the driving part has
Hub component 22 and load-bearing part 23.The driving part and damper quality part herein also can be via one or more spiral bullets
The spring element 6 of 7 form of spring overcomes its reset force to reverse, wherein the helical spring is contained in corresponding receiving portion 8 again.Spiral shell
Revolve spring 7 it is also as in the embodiment according to Fig. 1 herein in oriented like that along ring circumferential direction.
It also is provided with additional resetting apparatus 9 herein, the resetting apparatus has moving member or mobile 25 form of piston herein
Reset element 10, the moving member or mobile piston for example can radially move in guiding groove along linear guide apparatus 26
Dynamic, the guiding groove is formed on load-bearing part 23.Mobile piston 25 is radially outward pre-tightened via spring member 20, wherein described
Spring member is illustratively arranged herein, and the spring member is supported on the support 21 at load-bearing part 23 in side, and
And it is supported on mobile piston 25 in the other side.
The mobile piston has a concave portion 14 of arc on the outside, the female portion also formed herein for ball or
The guide rail 18 of roller 17, the ball or roller stick in the concave portion 15 being formed in quality loop 5 in the other side, institute
It states concave portion 15 and forms guide rail 19.Here, being therefore also again provided with the guide rail 18,19 to arch upward.
If quality loop 5 is reversed relative to driving part 2, it is on the one hand tensioned helical spring 7.On the other hand, roller
17 are rolled on the guide rail 18,19 being rotated relative to one another, accordingly, because mobile 25 one side of piston is via spring member
20, but on the other hand radially outward squeezed via existing centrifugal force, so being generated via resetting apparatus 9 additional multiple
Position force component.
Fig. 6 shows the embodiment according to the present invention of torsional vibration damper 1.The driving with hub component 3 is also showed that herein
Component 2 is bonded to leg spring 26 in shown example on the hub component, and the leg spring directly engages herein,
But it can also be engaged via hinge.Driving part 2 is arranged on axis herein, drives the driving part via the axis.
Leg spring 26 has leg 27, and guide rail 28 is equipped on the leg, and the guide rail arches upward.Rolling
Son 29 moves on the guide rail, and the roller is for example supported on damper Quality Mgmt Dept around fixed pivot axis
On part 4.When causing torsion by the vibration wait decay, in this roller 29 also in the leg spring 26 or leg 27 reversed relative to it
It is moved on its guide rail 28, causes the deformation of leg spring 26, leg 27 is radial to be slightly angled inwards, and reset force is thus caused
Generation.The first reset force component is generated as a result, is resetted force component via described first and is again resetted component 2 and 4.
It is radially outward squeezed in addition, leg 27 can also be acted on by centrifugal force.Therefore, in revolving speed height and higher feelings
Under condition, leg is radially outward squeezed, therefore is also pressed against roller 29.Turn as a result, since curved guide rail 28 generates basis
The reset force of speed, the reset force are additional reset force share.Therefore, through thus --- such as the embodiment party also described in front of
In formula like that --- the adaptive variations of the revolving speed of general reset power are also feasible.Therefore, leg spring 26 is additionally whereby
Also the resetting apparatus 9 for relatively causing reset force is formed, wherein leg 27 forms reset element 10.
In addition, showing four spring elements 6 of corresponding 7 form of helical spring, the spring element on the whole in Fig. 6
On the one hand it is supported on quality part 5, but is on the other hand supported on the corresponding support 30 at driving part 2.The bullet
The spring element 6 for the embodiment that spring element 6 describes before corresponding to.In the case where component 2 and 4 reverses relative to each other, spring
Two in element 6 are compressed respectively, and form corresponding reset force, and the reset force is acted on along ring circumferential direction.Another bullet
Spring element is correspondingly compressed to when being rotated in the opposite sense.
In the invention design scheme, therefore, to script, via leg spring realize damping unit additionally supplement edge
Furthermore the spring element 6 of ring circumferential direction setting, the damping unit are also provided according to centrifugal force or according to the reset force of revolving speed point
Amount.
Finally, Fig. 7 is shown below design scheme, wherein boss assembly 3 and leg additionally are arrived in the setting of another spring member 31
Between portion 27, the spring member illustratively helically form of spring 32 again, the helical spring support leg spring 26 or
The reset of leg 27.
Reference signs list
1 torsional vibration damper
2 driving parts
3 interior teeth portions
4 damper quality parts
5 quality loops
6 spring elements
7 helical springs
8 receiving portions
9 resetting apparatuses
10 reset elements
11 pivot rotaring levers
12 pivot axis
13 outsides
14 concave portions
15 concave portions
16 coupling elements
17 rollers/ball
18 guide rails
19 guide rails
20 spring members
21 supports
22 hub components
23 load-bearing parts
24 fulcrum posts
25 mobile pistons
26 leg springs
27 legs
28 guide rails
29 rollers
30 supports
31 spring members
32 helical springs.
Claims (10)
1. a kind of torsional vibration damper comprising the driving part (2) of pivot axis can be surrounded and the rotation axis can be surrounded
The damper quality part (4) that line is reversed relative to the driving part (2), which is characterized in that the damper quality part
(4) it can be resetted from the position deflected relative to the driving part (2) via reset force, the reset force is by least one
The spring element (6) compressed in torsion and at least one resetting apparatus (9) generation acted on according to centrifugal force.
2. torsional vibration damper according to claim 1, which is characterized in that the damper quality part (4) is via at least
One spring element (6) along the effect of ring circumferential direction couples, and the resetting apparatus (9) has at least one reset element
(10), the reset element can be moved radially according to centrifugal force, the reset element and damper quality part (4) coupling
Connection.
3. torsional vibration damper according to claim 2, which is characterized in that the reset element (10) is with can be pivotably
It is supported or can be moved linearly by, and coupled via coupling element and the damper quality part (4).
4. torsional vibration damper according to claim 3, which is characterized in that the reset element (10) is via at least one bullet
Spring component (20) is radially outward tensioned.
5. torsional vibration damper according to claim 4, which is characterized in that on the reset element (10) and/or in institute
Stating has the guide rail (18,19) to arch upward on damper quality part (8), the coupling element for being configured to roller (17) exists
It is rolled on the guide rail.
6. torsional vibration damper according to any one of claim 3 to 5, which is characterized in that reset element (10) structure
As pivot rods (11) or it is configured to linearly moving mobile piston (25).
7. torsional vibration damper according to claim 2, which is characterized in that the resetting apparatus (9) is arranged in the drive
Leg spring (26) on dynamic component (2), the leg spring is via coupling roller (29) and damper quality part (4) coupling
Connection, the roller that couples roll on the raceway (28) of the leg spring (26).
8. torsional vibration damper according to claim 7, which is characterized in that the spring element (6) is supported with an end
It is supported on the driving part (2) and with the other end on the damper quality part (4).
9. torsional vibration damper according to claim 7 or 8, which is characterized in that described equipped with other spring member (31)
The section with raceway (28) of the leg spring (26) is radially outward tensioned by other spring member.
10. torsional vibration damper according to any one of the preceding claims, which is characterized in that multiple spring elements (6) are enclosed
It is arranged in a distributed manner around ring week, the spring element is on identical radius or on different radiuses, and the bullet
The setting of spring element is arranged in one plane or with axially offsetting, and/or equipped with multiple resets around the distributed setting of ring week
Device (9).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102017114612.1 | 2017-06-30 | ||
| DE102017114612.1A DE102017114612A1 (en) | 2017-06-30 | 2017-06-30 | torsional vibration dampers |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109210133A true CN109210133A (en) | 2019-01-15 |
| CN109210133B CN109210133B (en) | 2021-11-26 |
Family
ID=64662066
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810558215.3A Active CN109210133B (en) | 2017-06-30 | 2018-06-01 | Torsional vibration damper |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN109210133B (en) |
| DE (1) | DE102017114612A1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1005744B (en) * | 1986-10-16 | 1989-11-08 | 琼·沃尔特沙·伊德公司 | The overload clutch of protection agricultural machinery power train |
| CN101061328A (en) * | 2004-11-20 | 2007-10-24 | 卢克摩擦片和离合器两合公司 | Torsional vibration damper |
| TW200819265A (en) * | 2006-09-07 | 2008-05-01 | Matheson Tri Gas | Torque limiting hand wheel |
| DE102010054303A1 (en) * | 2009-12-17 | 2011-06-22 | Schaeffler Technologies GmbH & Co. KG, 91074 | Two-mass flywheel for use in drive train of motor vehicle, has lever element tangentially rolled on inner circumference of flywheel mass by roller and pivotably mounted at flywheel mass, where lever element is designed with two-arms |
| WO2016073696A1 (en) * | 2014-11-08 | 2016-05-12 | Borgwarner Inc. | Rotational vibration damper |
| CN105683615A (en) * | 2013-10-31 | 2016-06-15 | Valeo离合器公司 | Mechanism for filtering torque fluctuations of a secondary member |
| WO2016120162A1 (en) * | 2015-01-29 | 2016-08-04 | Valeo Embrayages | Vibration damping device for a motor vehicle transmission chain |
| US20170089405A1 (en) * | 2015-09-30 | 2017-03-30 | Schaeffler Technologies AG & Co. KG | Synchronized wedge clutch with detent |
| WO2017072337A1 (en) * | 2015-10-30 | 2017-05-04 | Valeo Embrayages | Vibration damper, associated damping mechanism and propulsion assembly |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6142115A (en) | 1997-09-09 | 2000-11-07 | Luk Lamellen Und Kupplungsbau, Gmbh | Vibration damper for the crankshaft of a piston engine |
| DE102014223308A1 (en) | 2013-11-27 | 2015-05-28 | Schaeffler Technologies AG & Co. KG | Clutch disc with absorber unit |
-
2017
- 2017-06-30 DE DE102017114612.1A patent/DE102017114612A1/en not_active Withdrawn
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2018
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Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1005744B (en) * | 1986-10-16 | 1989-11-08 | 琼·沃尔特沙·伊德公司 | The overload clutch of protection agricultural machinery power train |
| CN101061328A (en) * | 2004-11-20 | 2007-10-24 | 卢克摩擦片和离合器两合公司 | Torsional vibration damper |
| TW200819265A (en) * | 2006-09-07 | 2008-05-01 | Matheson Tri Gas | Torque limiting hand wheel |
| DE102010054303A1 (en) * | 2009-12-17 | 2011-06-22 | Schaeffler Technologies GmbH & Co. KG, 91074 | Two-mass flywheel for use in drive train of motor vehicle, has lever element tangentially rolled on inner circumference of flywheel mass by roller and pivotably mounted at flywheel mass, where lever element is designed with two-arms |
| CN105683615A (en) * | 2013-10-31 | 2016-06-15 | Valeo离合器公司 | Mechanism for filtering torque fluctuations of a secondary member |
| WO2016073696A1 (en) * | 2014-11-08 | 2016-05-12 | Borgwarner Inc. | Rotational vibration damper |
| WO2016120162A1 (en) * | 2015-01-29 | 2016-08-04 | Valeo Embrayages | Vibration damping device for a motor vehicle transmission chain |
| US20170089405A1 (en) * | 2015-09-30 | 2017-03-30 | Schaeffler Technologies AG & Co. KG | Synchronized wedge clutch with detent |
| WO2017072337A1 (en) * | 2015-10-30 | 2017-05-04 | Valeo Embrayages | Vibration damper, associated damping mechanism and propulsion assembly |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109210133B (en) | 2021-11-26 |
| DE102017114612A1 (en) | 2019-01-03 |
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