CN101501363B - Method for reducing vibrations in a disc-shaped rotary component which is rotatable about a rotational axis, and rotary component - Google Patents
Method for reducing vibrations in a disc-shaped rotary component which is rotatable about a rotational axis, and rotary component Download PDFInfo
- Publication number
- CN101501363B CN101501363B CN200780028952.2A CN200780028952A CN101501363B CN 101501363 B CN101501363 B CN 101501363B CN 200780028952 A CN200780028952 A CN 200780028952A CN 101501363 B CN101501363 B CN 101501363B
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- Prior art keywords
- rotary member
- window
- max
- rotary component
- vibration
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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
Abstract
The invention relates to a method for reducing vibrations in a disc-shaped rotary component which is rotatable about a rotational axis, which rotary component is in sliding frictional contact, by means of a circular face which is coaxial with respect to the rotational axis, with a mating face of a mating component relative to which the rotary component rotates, in which method the rotary component is designed such that a cyclic symmetry which exists about the rotational axis of said rotary component is disrupted.
Description
Technical field
The present invention relates to the method for the vibration on a kind of rotary member of plate-like of rotating for reducing the rotation axis that rotates, the rotary member of this plate-like contacts with respect to the fitting surface of the rounded face of this coaxial heart and the mating component mode with sliding friction with one, and this rotary member rotates with respect to this mating component.
In addition, the present invention relates to a kind of rotary member of plate-like, the rotary member of this plate-like can rotate in the mounting point that rotation axis is rotated and can contact with respect to the fitting surface of the rounded face of this coaxial heart and the mating component mode with sliding friction with one, and this rotary member can be with respect to this mating component rotation.
Background technique
When having rubbing contact between fitting surface and the rotary member that rotates with respect to fitting surface, vibration, especially to can be used as vibration that squish hears in audio range be problem widely in the technology.The exemplary of this vibration of hearing is the braking squish, and this braking squish occurs in rail vehicle, but also occurs in Motor Vehicle.
For many years effect differently is devoted to the elimination of this vibration.
Summary of the invention
Task of the present invention is, provides the solution possibility of described vibration problem.
This task solves by the method for the vibration on a kind of rotary member of plate-like of rotating for reducing the rotation axis that rotates, the rotary member of this plate-like contacts with respect to the fitting surface of the rounded face of the coaxial heart and the mating component mode with sliding friction with one, rotary member rotates with respect to this mating component, in the method, construct like this rotary member: so that the Cyclic Symmetry that exists around the rotation axis of this rotary member is interfered.
Be configured to generally planar, the rotation axis that can rotate is rotated, can be membrance-type structure components with the rotary member of the fitting surface rubbing contact of the rounded face of a concentric and a mating component, described membrance-type structure components can be energized multiple mode of vibration, and the rounded face of described concentric can be outside circumferential surface or the face that axially points to.That the contact of sliding friction mode can cause having same form but have between the mode of the position of tangential position opposite on the sense of rotation or opposition and have the feedback coupling, wherein, this mode has identical natural frequency.The feedback coupling that has between this mode of same frequency causes unstability.
Verified in large-scale research, feedback coupling (R ü ckkopplung) mode of the paired appearance of rotary member is connected each other and therefore the Cyclic Symmetry of rotary member play an important role.
The frequency that the interference of Cyclic Symmetry is made the mode that is fed coupling separately, thus, condition of instability is interfered and the generation vibrated is reduced or suppressed to a great extent.
Rotary member advantageously is provided with the deception equipment of arranging asymmetrically and/or be shaped asymmetrically along circumferencial direction, and the quantity value of described deception equipment is m, and wherein, n/m is not integer, and n is the symmetrical cycle quantity of rotary member.
Can rotate in the mounting point that rotation axis is rotated and can contact with respect to the fitting surface of the rounded face of the coaxial heart and the mating component mode with sliding friction with one according to the rotary member of plate-like of the present invention, rotary member can rotate with respect to this mating component, and the Cyclic Symmetry that this rotary member is configured to rotate around it axis is interfered.
Rotary member is advantageously provided the window of arranging asymmetrically in a circumferential direction and/or construct asymmetrically toward each other, and the quantity of described window is m, and wherein exist: n/m is not integer, the symmetrical cycle quantity of n=rotary member.
The size of window advantageously satisfies following relationship: each window width in a circumferential direction is greater than 5 degree; The radial length of each window is greater than 10% of the radial length of rotary member in the zone of this window.
Layout for window advantageously is suitable for following relationship:
-nonsymmetry radially
-tangential nonsymmetry ΔΦ
Max-ΔΦ
Min＞10 °, wherein,
R
i,
Be window i (i=1 ..., the radial position of m) " center of gravity " and tangential position and
R
max＝max{R
i}，R
min＝min{R
i}，i＝1，...，m；
ΔΦ
max＝max{ΔΦ
i}，ΔΦ
min＝min{ΔΦ
min}，i＝1，...，m。
The present invention be used in all types to a great extent be excited to natural vibration, especially can be excited to have a same form but have the member of the natural vibration of opposite in a circumferential direction tangential position or position.This member preferably for example for example makes this dish be out of shape the member that method is out made from its face by arching, extruding or other by the planar disk with different in case of necessity thickness.Dish also can keep plane, for example brake disc.
The present invention can be advantageously used in the seal membrane on the double mass flywheel.
Description of drawings
The below exemplarily and in further detail describes the present invention by means of schematic figures.Accompanying drawing represents:
Two mode of vibration, in a circumferential direction position opposite of Fig. 1 and a circle ring disk of Fig. 2;
Seal membrane of Fig. 3, sealing diaphragm at the first dish of inner radial and double mass flywheel without being connected with relatively rotating, radially outer in axial pre-situation about clamping with the second dish rubbing contact;
Fig. 4, Fig. 6, Fig. 8 and Figure 10 have three embodiments of the seal membrane of different window numbers;
Fig. 5, Fig. 7, Fig. 9 and Figure 11 belong to the natural vibration eigenvalue of Fig. 4, Fig. 6, Fig. 8 and Figure 10; And
Each four windows, two kinds of different setting type in a seal membrane of Figure 12 and Figure 13.
Embodiment
Fig. 1 shows the slightly microsomal view of a circle ring disk, and this circle ring disk is preferably configured as flat and has compares little thickness with its diameter.But circle ring disk 20 plane earths or arching ground orientation, this circle ring disk has internal diameter R
1With external diameter R
2Circle ring disk within it footpath is gone up clamped and fixing and is being rested in the situation of radially preload on its external diameter on the cylindrical internal surface that arranges with respect to circle ring disk 20 coaxial hearts, and this cylindrical body rotates.Scheme as an alternative, also can arrange like this: the cylindrical body position is fixed, and circle ring disk rotates.
Owing to radially pre-clamp exist in the plane that is in circle ring disk, perpendicular to the normal force of the external diameter of this circle ring disk.The tangential force that exists the tangential direction at circle ring disk to work owing to sliding contact.
Circle ring disk is one can be energized to get the member of vibration, and wherein, the natural mode of vibration of circle ring disk vibration has following formula:
Wherein, r, ρ are the coordinates in the cylindrical-coordinate system, n
1=0,1,2 ..., n
2=0,1,2 ..., be integer.
At n
2This mode in ≠ 0 the situation has n along circumference
2There are respectively a node of oscillations in individual arching and depression or plane of vibration between them.Especially when exist for each mode one have same frequency " to "
The time unstability of vibration appears, wherein, the arching of a mode and depression are in the position that another mode has node of oscillations just.
Fig. 1 respectively shows a vibration antinode in the above and below of this figure with dark color, and wherein, nodal line is horizontal-extending between antinode.Fig. 2 shows paired mode, and in this paired mode, opposite each other on horizontal line with the dark vibration antinode 22 that represents, unshowned nodal line vertically extends.
If circle ring disk is with the modal vibration according to Fig. 1 and Fig. 2, then at genetic method in the situation of circle ring disk circumference rubbing contact to the variation of power, this changes in the zone of vibration antinode maximum, and is minimum in the zone of node of oscillations.The variation of normal force causes tangential force to change.There is the feedback coupling thus in the mode that the variable effect of tangential force occurs in pairs between the mode that occurs in pairs.In undamped situation, this mode is unstable.
The axial deformation of dish causes the variation of normal force generating period.Because friction, this cyclically-varying of normal force causes the variation of tangential force generating period.Tangential variations does not cause that axial force changes, and thus, the stiffness matrix of system is asymmetric under friction condition.
The natural frequency of mechanical system can be expressed as plural number, and wherein, the imaginary part of plural number represents vibration frequency, and real part is described stability.If all the real part of natural frequency is for bearing or equalling zero, then system stability.The natural frequency that positive real part occurs having then means unstable.
In undamped situation, has the system stability of symmetrical stiffness matrix.This system only has the natural frequency that real part is null value.In the asymmetric situation of stiffness matrix, the real part of some natural frequencys can be not equal to zero.
Under investigating the asymmetric situation of stiffness matrix, can study with the stability in the system of friction the analysis of multiple natural frequency.Adopting the ANSYS 10.0 of Q-R damped method modal analysis is a program, can implement this analysis by this program.The analysis of multiple natural frequency not only can realize qualitative explanation, and can realize quantitative explanation.The size of the real part λ of multiple natural frequency shows how corresponding natural mode of vibration amplitude changes.Zero real part (λ=0) means constant Oscillation Amplitude; If λ is not equal to zero, then there is representation A (t)=A
0E
λ t, this representation represents the Oscillation Amplitude with time correlation.λ＞0 means vibration enhancing, namely unstable, and λ＜0 means vibration weakening.
The real part of natural frequency, the especially natural frequency not only nonsymmetry with stiffness matrix is relevant, and relevant with damping.In having contact friction or reclining the system that rubs, damping is non-steadiness parameter, because damping is along with vibration frequency and amplitude, friction factor, impacting force and other a plurality of factors change.Therefore, can not accurately introduce damping in the modal analysis of Q-R damped method, modal analysis is carried out in the situation of not considering damping.In undamped system with the size of the real part of the positive sign instable criterion as different natural mode of vibration.
The hypothesis friction factor is 0.5 in calculating because when friction factor in contact because the material removal of part raises until μ=0.5～0.6 the time, squish appears when turntable (Drehbank) is tested.Proper value analyzed processing in the frequency range (seal membrane squish frequency typically is between 2000 to 8000Hz) of maximum 10000Hz.
The below is described in its application facet on seal membrane above-mentioned thinking, and the sealing diaphragm is as for example using in the double mass flywheel described in DE 100 02 259 A1.This seal membrane is the annular disk of preferable alloy, this annular disk for example is rigidly connected by rivet with the first dish of double mass flywheel on section's circumferential area within it, this annular disk from the inner radial zone that it is riveted in the axial direction arching and its radially outer zone in axial pre-situation about clamping with the second dish of double mass flywheel rubbing contact slidably, this second dish is being supported with respect to the coaxial heart of the first dish and can reversing a restricted amount with respect to the first dish.
Fig. 3 shows such situation with plan view:
Consist of the circular seal membrane of rotary member with 30 marks, the sealing diaphragm on the zone 32 of its circular inner radial by the join domain painted with dark color for example rivet is connected with a dish 32 of unshowned double mass flywheel and zone 34 at its radially outer on another dish of double mass flywheel rubbing contact slidably.Rubbing contact part preferred axes is to pre-clamping, but also can radially clamp in advance.Structure is fenestrate 36 in seal membrane, is discussed in more detail below the task of these windows.Window 36 has elongation Δ Ri radially, and wherein, i is corresponding to separately window, and has the in a circumferential direction elongation on angular regions
The radial width value of circle ring disk 20 is H.
Fig. 4 shows the setting type of Fig. 3, and seal membrane 30 is windowless and double mass flywheel can rotate generally, and rotation axis X rotates or seal membrane 30 can correspondingly rotate that rotation axis X rotates with respect to one of dish.
Fig. 5 shows the characteristic curve of vibration characteristics of the seal membrane 30 of Fig. 4.Abscissa is described the frequency of natural vibration, and unit is Hz.Y coordinate is described the value λ that illustrates the previously natural frequency of λ＞0 (only for), and unit is second
-1As can be seen, have a plurality of unsettled natural frequencys or mode of vibration, these unsettled natural frequencys or mode of vibration satisfy the above-mentioned condition of energy interchange and consist of thus the inducement of the squish that can hear.
Fig. 6 shows a kind of setting type, and in this setting type, seal membrane 30 is provided with a window 36.Only obtain nine natural frequencys with positive real part after the layout of Optimal Window and size in 0 to 10000Hz scope, its maximum value is approximately 44.4 seconds
-1(Fig. 7).
If according to Fig. 8 two windows are set, then after the position of optimizing these windows and size, only obtain two proper values with positive real part according to Fig. 9, its maximum value is 26.4 seconds
-1
Arrange in the situation of three windows in layout and size with Figure 10, obtain three natural frequencys with positive real part according to Figure 11, its maximum value only value is 5.6 seconds
-1
In the situation of four windows (Figure 12 and Figure 13), seal membrane can be constructed to get complete stability in 0 to 10000Hz scope, does not namely have the proper value with positive real part.At this, in Figure 12 and Figure 13, two different possible window setting types have been shown.
Applicablely for the layout of the size of window number, window and window be: the purpose of arranging window is to disturb axial Cyclic Symmetry, makes thus the frequency of feedback coupled mode different.For this reason, the possibility that existence itself is extremely different, for example variation of supporting, the variation of member face, the variation of member thickness, the variation of mass area ratio, etc.Be provided for disturbing symmetric window or otch to be proved to be very effective.
1. window is counted m:
For the Cyclic Symmetry member with loop number=n, ratio n/m should not be integer.
Minimum number value for the window of axial symmetrical component (n=1) is m=2.For have Cyclic Symmetry supporting shown in the seal membrane value be n=6 the result of study of research example ().The minimum number of window so value are m=4, because at m=1,2 or 3 o'clock, n/m=6,3 or 2.
2. the size of window:
The tangential width of each window (angular range) value should greater than
The radial length Δ R value of each window should be greater than 10% of the radial dimension H of seal membrane.
3. asymmetric layout:
Suppose R
iWith
Be the radial position of center of gravity of window i and tangential position and
R
max＝max{R
i}，R
min＝min{R
i}，i＝1，...，m；
ΔΦ
max＝max{ΔΦ
i}，ΔΦ
min＝min{ΔΦ
min}，i＝1，...，m，
Then should satisfy following condition:
-nonsymmetry radially
-tangential nonsymmetry ΔΦ
Max-ΔΦ
Min＞10 °.
Thus, window is not only at it toward each other aspect the position but also constructing asymmetricly aspect its configuration.
The optimum size of window on the one hand should be not too small, so because the instable impact to be eliminated of vibration characteristics is become too small, on the other hand because the strength and stiffness of diaphragm and should be not excessive.Window should be checked by calculating the instable impact of vibration characteristics.
After the quantity of having determined window, the size of the radial position of Optimal Window and tangential position and window is in order to minimize the quantity with positive real part and the peaked proper value of real part.
The check of the effectiveness of these measures not only by studying to carry out with the Q-R damped method modal analysis in ANSYS 10.0 programs or with the numeral that the similar approach in other program is implemented, and is undertaken by direct research acoustic characteristic on test stand.
Can use at the whole members that rotate around axis by means of the method according to this invention that its application on a seal membrane of axially installing to pre-clamping is described, described member contacts with the mode of another member with sliding friction, wherein, frictional force can work at radial direction or the axial direction of the member that rotates.The concept of the member of plate-like comprises at this can be by dish be shaped the tank shape that or the member of cap shape.
The natural mode of vibration of paired appearance is carried out autotelic interference be proved to be than the effective developing instrument of common method so far, attempt so far generation with the creak noise in the common method owing to stick-slip phenomenon at these.
The reference number inventory
20 circle ring disks
22 vibration antinode
30 seal membranes
32 zones
34 zones
36 windows
Claims (7)
1. the method for the vibration on the rotary member of the plate-like of rotating for reducing the rotation axis that rotates, the rotary member of this plate-like contacts with respect to the fitting surface of the rounded face of this coaxial heart and the mating component mode with sliding friction with one, this rotary member rotates with respect to this mating component, in the method, construct like this this rotary member: so that the Cyclic Symmetry that exists around the rotation axis of this rotary member is interfered by window or the otch that is formed on the described rotary member.
2. according to claim 1 method, in the method, this rotary member is provided with the deception equipment of arranging asymmetrically and/or be shaped asymmetrically along circumferencial direction, described deception equipment is configured as described window or otch, the quantity value of described deception equipment is m, wherein, n/m is not integer, and n is the quantity of the symmetrical cycle of this rotary member.
3. the rotary member of plate-like (30), the rotary member of this plate-like can rotate in the mounting point that rotation axis is rotated and can contact with respect to the fitting surface of the rounded face of this coaxial heart and a mating component (34) mode with sliding friction with one, this rotary member can rotate with respect to this mating component, and the Cyclic Symmetry that this rotary member is configured to rotate around it axis is interfered by window or the otch that is formed on the described rotary member.
4. according to claim 3 rotary member, this rotary member is provided with the window (36) of arranging asymmetrically in a circumferential direction and/or construct asymmetrically toward each other, the quantity of described window is m, and wherein: n/m is not integer, the quantity of the symmetrical cycle of this rotary member of n=.
5. according to claim 4 rotary member, wherein, the size of described window satisfies following relationship: each window (36) width in a circumferential direction is greater than 5 degree; The radial length of each window (36) is greater than 10% of the radial length of this rotary member in the zone of this window.
6. according to claim 4 or 5 rotary member, wherein, for the applicable following relationship of the layout of described window:
Nonsymmetry radially
Tangential nonsymmetry Δ Ф
Max-Δ Ф
Min＞10 °, wherein,
R
i,
Be window i (i=1 ..., radial position and the tangential position of m) " center of gravity ", and
R
max＝max{R
i}，R
min＝min{R
i}，i＝1，...，m；
ΔФ
max＝max{ΔФ
i}，ΔФ
min＝min{ΔФ
i}，i＝1，...，m；
Wherein H is the radial width of the rotary member of plate-like.
7. according to claim 3 to one of 5 rotary member, this rotary member is the seal membrane (30) on the double mass flywheel (32), wherein, the sealing diaphragm on the fringe region of the fringe region of its inner radial or radially outer without relatively rotate with two of this double mass flywheel coaxially to each other the heart setting, one of can the restricted toward each other dish that reverses be connected and with the fringe region elasticity preload of the fringe region of its radially outer or inner radial rest on another of these dish.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102006036206 | 2006-08-03 | ||
| DE102006036206.3 | 2006-08-03 | ||
| PCT/DE2007/001241 WO2008014744A2 (en) | 2006-08-03 | 2007-07-12 | Method for reducing vibrations in a disc-shaped rotary component which is rotatable about a rotational axis, and rotary component |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101501363A CN101501363A (en) | 2009-08-05 |
| CN101501363B true CN101501363B (en) | 2013-04-17 |
Family
ID=38997499
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200780028952.2A Expired - Fee Related CN101501363B (en) | 2006-08-03 | 2007-07-12 | Method for reducing vibrations in a disc-shaped rotary component which is rotatable about a rotational axis, and rotary component |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN101501363B (en) |
| DE (1) | DE112007001664A5 (en) |
| WO (1) | WO2008014744A2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101786314B1 (en) * | 2016-03-21 | 2017-10-17 | 현대자동차주식회사 | Dynamic damper assembly |
| CN109543241B (en) * | 2018-10-30 | 2023-07-14 | 浙江万向系统有限公司 | Automatic identification method for standard normal mode of brake disc |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5295411A (en) * | 1993-06-22 | 1994-03-22 | Speckhart Frank H | Torsional vibration absorber system |
| CN1284617A (en) * | 1995-07-24 | 2001-02-21 | 株式会社艾科赛迪 | Damping disc assembly having friction mechanism with improved friction piece |
| CN1302749A (en) * | 1999-10-29 | 2001-07-11 | 现代自动车株式会社 | Vibrating attennuation equipment for damping spring of clutch disk and method thereof |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59187134A (en) * | 1983-04-06 | 1984-10-24 | Matsushita Electric Ind Co Ltd | Flywheel |
| JPH01312245A (en) * | 1988-06-13 | 1989-12-18 | Nissan Motor Co Ltd | Constant order type dynamic damper |
| DE19534818A1 (en) * | 1995-09-20 | 1997-03-27 | Hasse & Wrede Gmbh | Crankshaft vibration absorber for internal combustion piston engine |
| RU2232929C2 (en) * | 2001-12-18 | 2004-07-20 | Папук Светлана Николаевна | Flywheel with center of mass displaced relative to axis of rotation |
| GB2413614A (en) * | 2004-05-01 | 2005-11-02 | Safe Developments Ltd | A flywheel with pendulum masses tracking an order of vibration across engine speeds |
-
2007
- 2007-07-12 CN CN200780028952.2A patent/CN101501363B/en not_active Expired - Fee Related
- 2007-07-12 DE DE112007001664T patent/DE112007001664A5/en not_active Withdrawn
- 2007-07-12 WO PCT/DE2007/001241 patent/WO2008014744A2/en active Application Filing
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5295411A (en) * | 1993-06-22 | 1994-03-22 | Speckhart Frank H | Torsional vibration absorber system |
| CN1284617A (en) * | 1995-07-24 | 2001-02-21 | 株式会社艾科赛迪 | Damping disc assembly having friction mechanism with improved friction piece |
| CN1302749A (en) * | 1999-10-29 | 2001-07-11 | 现代自动车株式会社 | Vibrating attennuation equipment for damping spring of clutch disk and method thereof |
Non-Patent Citations (1)
| Title |
|---|
| JP平1-312245A 1989.12.18 |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2008014744A3 (en) | 2008-06-26 |
| DE112007001664A5 (en) | 2009-04-30 |
| CN101501363A (en) | 2009-08-05 |
| WO2008014744A2 (en) | 2008-02-07 |
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