CN113265911A - Elastic strip dynamic vibration absorber - Google Patents
Elastic strip dynamic vibration absorber Download PDFInfo
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- CN113265911A CN113265911A CN202110388373.0A CN202110388373A CN113265911A CN 113265911 A CN113265911 A CN 113265911A CN 202110388373 A CN202110388373 A CN 202110388373A CN 113265911 A CN113265911 A CN 113265911A
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- 239000006096 absorbing agent Substances 0.000 title claims abstract description 79
- 238000013016 damping Methods 0.000 claims abstract description 59
- 239000000463 material Substances 0.000 claims abstract description 10
- 229910000831 Steel Inorganic materials 0.000 claims abstract description 7
- 238000010521 absorption reaction Methods 0.000 claims abstract description 7
- 239000000853 adhesive Substances 0.000 claims abstract description 7
- 230000001070 adhesive effect Effects 0.000 claims abstract description 7
- 239000010959 steel Substances 0.000 claims abstract description 7
- 238000004458 analytical method Methods 0.000 claims description 7
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- 230000008878 coupling Effects 0.000 claims description 3
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- 230000002401 inhibitory effect Effects 0.000 abstract description 3
- 238000004519 manufacturing process Methods 0.000 abstract description 3
- 238000009434 installation Methods 0.000 description 6
- 230000002829 reductive effect Effects 0.000 description 6
- 230000001133 acceleration Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
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- 201000010099 disease Diseases 0.000 description 1
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- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
- E01B19/00—Protection of permanent way against development of dust or against the effect of wind, sun, frost, or corrosion; Means to reduce development of noise
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- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
- E01B19/00—Protection of permanent way against development of dust or against the effect of wind, sun, frost, or corrosion; Means to reduce development of noise
- E01B19/003—Means for reducing the development or propagation of noise
-
- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
- E01B9/00—Fastening rails on sleepers, or the like
- E01B9/02—Fastening rails, tie-plates, or chairs directly on sleepers or foundations; Means therefor
- E01B9/28—Fastening on wooden or concrete sleepers or on masonry with clamp members
- E01B9/30—Fastening on wooden or concrete sleepers or on masonry with clamp members by resilient steel clips
- E01B9/303—Fastening on wooden or concrete sleepers or on masonry with clamp members by resilient steel clips the clip being a shaped bar
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- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
- E01B9/00—Fastening rails on sleepers, or the like
- E01B9/02—Fastening rails, tie-plates, or chairs directly on sleepers or foundations; Means therefor
- E01B9/32—Fastening on steel sleepers with clamp members
- E01B9/34—Fastening on steel sleepers with clamp members by resilient steel clips
-
- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
- E01B2201/00—Fastening or restraining methods
- E01B2201/08—Fastening or restraining methods by plastic or elastic deformation of fastener
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- Engineering & Computer Science (AREA)
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- Structural Engineering (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
Abstract
A spring dynamic vibration absorber relates to the railway safety field and comprises an elastic damping layer and a rigid layer; a first mounting hole for the elastic wall of the elastic strip to penetrate through is formed in the center of the elastic damping layer, the inner diameter and the outer diameter of the elastic damping layer are respectively 15 mm and 30mm, soft rubber is selected as a material, and the elastic modulus is 6 MPa; a second mounting hole for mounting the elastic damping layer is formed in the center of the rigid layer, the inner diameter and the outer diameter of the rigid layer are respectively 30mm and 45mm, and steel is selected as a material; the elastic damping layer and the rigid layer are connected through an adhesive to form a dynamic vibration absorption structure with the thickness of 10 mm. The elastic strip dynamic vibration absorber is convenient to install and low in manufacturing cost, does not affect other performances of a fastener system and an elastic strip, can be used as a better mode for inhibiting the elastic strip from being broken by resonance, absorbs the resonance energy of a structure by virtue of a self spring-damping system, and finally consumes the resonance energy by virtue of a self damping element, and belongs to a passive vibration controller.
Description
Technical Field
The invention relates to the field of railway safety, in particular to an elastic strip dynamic vibration absorber.
Background
The clip system is an important component of the track structure and functions to secure the rail to the tie, maintain gauge and prevent longitudinal and lateral movement of the rail relative to the tie. The spring strips are part of a fastener system that provides a fastening force by buckling the rail. In recent years, many high-speed railway lines and urban rail transit lines have been constructed and put into operation. Along with the increase of operation time, more and more track system diseases appear, and fastener bullet strip takes place extensive fracture, seriously influences train operation security performance. A large number of researches show that the resonance of the elastic strip can be caused by the high-frequency wheel rail excitation generated by rail corrugation and polygonal wheels, the response of the elastic strip is increased due to the resonance, the stress change amplitude is increased, the fatigue life is shortened, and the elastic strip is abnormally broken.
The structure dynamic vibration absorber is characterized in that a weight with certain mass is placed on a structure and supported by a spring and a damping, the spring and the damping constant are adjusted to tune with the natural frequency of the structure, and the vibration of the structure can be controlled by taking the inertia force of the weight as a reaction force. According to the principle, the elastic strip dynamic vibration absorber is designed to restrain the resonance peak value of the elastic strip, so that the stress of the elastic strip is reduced, the service fatigue life of the elastic strip is prolonged, the abnormal fracture of the elastic strip is reduced, and the safe operation of a train can be guaranteed.
Disclosure of Invention
Objects of the invention
In order to solve the technical problems in the background art, the invention provides an elastic strip dynamic vibration absorber. The elastic strip dynamic vibration absorber is used as an additional part of an elastic strip and is arranged in a section with more broken elastic strips, the installation is convenient, the manufacturing cost is low, other performances of a fastener system and the elastic strip are not influenced, the elastic strip dynamic vibration absorber can be used as a better mode for inhibiting the elastic strip from being broken by resonance, the resonance energy of a structure is absorbed by a self spring-damping system, and finally the consumption is carried out by a self damping element, the elastic strip dynamic vibration absorber belongs to a passive vibration controller, and meanwhile, the parameter design of the elastic strip dynamic vibration absorber is carried out by the dynamic vibration absorption principle, so that the vibration response of the elastic strip can be reduced in an expected frequency range, and the aim of prolonging the fatigue life is fulfilled.
(II) technical scheme
In order to solve the above problems, the present invention provides a spring dynamic vibration absorber, which comprises an elastic damping layer and a rigid layer; a first mounting hole for the elastic wall of the elastic strip to penetrate through is formed in the center of the elastic damping layer, the inner diameter and the outer diameter of the elastic damping layer are respectively 15 mm and 30mm, soft rubber is selected as a material, and the elastic modulus is 6 MPa; a second mounting hole for mounting the elastic damping layer is formed in the center of the rigid layer, the inner diameter and the outer diameter of the rigid layer are respectively 30mm and 45mm, and steel is selected as a material; the elastic damping layer and the rigid layer are connected through an adhesive to form a dynamic vibration absorption structure with the thickness of 10 mm.
Preferably, the structure of the elastic damping layer and the rigid layer includes a circular ring shape-circular ring shape, a circular ring shape-polygon shape, but is not limited to the above structural forms.
Preferably, the elastic damping layer and the elastic strip are connected by an adhesive.
Preferably, the steel material selected has a density of 7850kg/m3。
The invention also provides a parameter design method of the elastic strip dynamic vibration absorber, which comprises the following steps:
s1, dispersing the continuous structure of the fastener elastic strip into a non-coupling multi-freedom-degree model formed by combining a plurality of single-freedom-degree systems by adopting a modal analysis technology and according to the orthogonality of modal vectors, wherein the equivalent mass of the ith-order mode of the fastener elastic strip is as shown in a formula (1):
in the formula: miRepresenting the equivalent mass of the jth degree of freedom of the fastener elastic strip relative to the ith order mode; t istThe kinetic energy of the whole fastener elastic strip is obtained; (x)1,x2,···xj,···xN) The intrinsic vector represents the ith order mode of the fastener elastic strip; (m)1,m2,···mj,···mN) Is a discrete single degree of freedom mass; omegaiIs the ith order natural circle frequency;
s2, after the equivalent mass of the elastic strip is obtained, the equivalent rigidity of the elastic strip of the fastener in the ith-order mode can be obtained by the following formula (2):
and S3, obtaining the optimal parameters of the ith-order modal additional dynamic vibration absorber of the elastic strip of the fastener by utilizing a formula of the optimal harmony and optimal damping conditions of the single degree of freedom of the damping main system.
Preferably, the specific steps of S3 are as follows:
(1) calculate the mass of the fastener spring strip with dynamic vibration absorber, see formula (3)
mi＝μiMi (3)
(2) Calculating the optimal spring rate of the fastener elastic strip additional dynamic vibration absorber, see formula (4)
(3) Optimal damping coefficient of fastener elastic strip additional dynamic vibration absorber, see formula (5)
In the above formula,. mu.iIs the mass ratio; m isiRepresenting the mass of the fastener elastic strip ith-order modal dynamic vibration absorber; miRepresenting the i-th order modal equivalent mass of the fastener elastic strip; kiRepresenting the i-th order modal equivalent stiffness of the elastic strip of the fastener; k is a radical ofiRepresenting the optimal rigidity of the fastener elastic strip ith-order modal dynamic vibration absorber; c. CiRepresenting the optimal damping of the fastener elastic strip ith-order modal dynamic vibration absorber; ziRepresenting the ith order modal equivalent damping of the fastener elastic strip; zetaiThe i-th order modal equivalent damping ratio of the fastener elastic strip is shown.
The technical scheme of the invention has the following beneficial technical effects:
the elastic strip dynamic vibration absorber is used as an additional part of an elastic strip and is arranged in a section with more broken elastic strips, the installation is convenient, the manufacturing cost is low, other performances of a fastener system and the elastic strip are not influenced, the elastic strip dynamic vibration absorber can be used as a better mode for inhibiting the elastic strip from being broken by resonance, the resonance energy of a structure is absorbed by a self spring-damping system, and finally the consumption is carried out by a self damping element, the elastic strip dynamic vibration absorber belongs to a passive vibration controller, and meanwhile, the parameter design of the elastic strip dynamic vibration absorber is carried out by the dynamic vibration absorption principle, so that the vibration response of the elastic strip can be reduced in an expected frequency range, and the aim of prolonging the fatigue life is fulfilled.
Drawings
Fig. 1 is a schematic view of a first structure of a spring dynamic vibration absorber according to the present invention.
Fig. 2 is a schematic diagram of a second structure of the elastic strip dynamic vibration absorber according to the present invention.
Fig. 3 is a schematic view of a first structural structure of the elastic strip dynamic vibration absorber and an installation structure of an omega-shaped elastic strip according to the present invention.
Fig. 4 is a second structural structure of the elastic strip dynamic vibration absorber and an installation structure diagram of an omega-shaped elastic strip according to the present invention.
Fig. 5 is a first structural structure of the elastic strip dynamic vibration absorber and an installation structural diagram of an e-shaped elastic strip according to the present invention.
Fig. 6 is a second structural structure of the elastic strip dynamic vibration absorber and an installation structure diagram of an e-shaped elastic strip according to the present invention.
Fig. 7 is a graph comparing the acceleration frequency response function of the original elastic strip and the elastic strip with the dynamic vibration absorber.
Description of the drawings: 1. a spring bar; 2. an elastic damping layer; 3. a rigid layer.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be described in further detail with reference to the accompanying drawings in conjunction with the following detailed description. It should be understood that the description is intended to be exemplary only, and is not intended to limit the scope of the present invention. Moreover, in the following description, descriptions of well-known structures and techniques are omitted so as to not unnecessarily obscure the concepts of the present invention.
Example 1
The invention provides a parameter design method of a spring strip dynamic vibration absorber, which comprises the following steps:
s1, dispersing the continuous structure of the fastener elastic strip into a non-coupling multi-freedom-degree model formed by combining a plurality of single-freedom-degree systems by adopting a modal analysis technology and according to the orthogonality of modal vectors, wherein the equivalent mass of the ith-order mode of the fastener elastic strip is as shown in a formula (1):
in the formula: miRepresenting the equivalent mass of the jth degree of freedom of the fastener elastic strip relative to the ith order mode; t istThe kinetic energy of the whole fastener elastic strip is obtained; (x)1,x2,···xj,···xN) The intrinsic vector represents the ith order mode of the fastener elastic strip; (m)1,m2,···mj,···mN) Is a discrete single degree of freedom mass; omegaiIs the ith order natural circle frequency;
s2, after the equivalent mass of the elastic strip is obtained, the equivalent rigidity of the elastic strip of the fastener in the ith-order mode can be obtained by the following formula (2):
and S3, obtaining the optimal parameters of the ith-order modal additional dynamic vibration absorber of the elastic strip of the fastener by utilizing a formula of the optimal harmony and optimal damping conditions of the single degree of freedom of the damping main system.
In an alternative embodiment, the specific steps of S3 are as follows:
(1) calculate the mass of the fastener spring strip with dynamic vibration absorber, see formula (3)
mi＝μiMi (3)
(2) Calculating the optimal spring rate of the fastener elastic strip additional dynamic vibration absorber, see formula (4)
(3) Optimal damping coefficient of fastener elastic strip additional dynamic vibration absorber, see formula (5)
In the above formula,. mu.iIs the mass ratio; m isiRepresenting the mass of the fastener elastic strip ith-order modal dynamic vibration absorber; miRepresenting the i-th order modal equivalent mass of the fastener elastic strip; kiRepresenting the i-th order modal equivalent stiffness of the elastic strip of the fastener; k is a radical ofiRepresenting the optimal rigidity of the fastener elastic strip ith-order modal dynamic vibration absorber; c. CiRepresenting the optimal damping of the fastener elastic strip ith-order modal dynamic vibration absorber; ziRepresenting the ith order modal equivalent damping of the fastener elastic strip; zetaiThe i-th order modal equivalent damping ratio of the fastener elastic strip is shown.
From the above, it can be seen that the mass ratio μ of the dynamic vibration absorber is giveniEquivalent mass M of fastener elastic strip ith order modeiEquivalent stiffness KiAnd equivalent damping ZiAnd the optimal rigidity and damping of the fastener elastic strip ith-order modal dynamic vibration absorber can be determined. According to the equivalent mass calculation formulas (1) and (3), when the j point isWhen the position of the maximum deformation of the mode of the elastic strip of the fastener is the antinode position of the mode, the mode equivalent mass is minimum at the moment, and the mass ratio is maximum; when the j point is at the point where the modal deformation of the fastener elastic strip is zero, namely the node position, the modal equivalent mass is infinite at the moment, and the mass ratio is equal to zero. According to the passive vibration absorption principle, the vibration attenuation amplitude of the main system of the elastic strip and the mass ratio are in a direct proportion relationship, and the larger the mass ratio is or the smaller the modal equivalent mass is, the larger the vibration attenuation of the elastic strip is. Therefore, the optimal position of the fastener elastic strip dynamic vibration absorber is the antinode position of the vibration mode, namely the highest point of the elastic strip elastic arm.
Example 2
Because the mode of the elastic strip is mainly the first two orders, the vibration mode is represented by vertical vibration of the elastic strip elastic arm, and the left and right elastic arm vibrations of the first order and the second order are respectively symmetrical and antisymmetric. Therefore, when designing the elastic strip dynamic vibration absorber, only the design of the dynamic vibration absorber for controlling the first-order mode of the elastic strip is considered. The first-order equivalent mass of the elastic strip obtained by modal analysis calculation is 0.45kg, and the equivalent stiffness is 4.8 kN/mm. The optimal parameters of the dynamic vibration absorber for controlling the 1 st order mode of the elastic strip can be obtained by the above given equivalent mass and equivalent stiffness solving formula of the 1 st order mode of the elastic strip of the fastener. The final mass ratio was taken to be 0.3, the mass of the vibration absorber was taken to be 0.14kg, the stiffness was taken to be 2.22kN/mm, and the damping was taken to be 207N · s/m. The frequency of the omega-type elastic strip 1 is about 500Hz, the natural frequency of the e-type elastic strip 1 is 800Hz, and the design parameters of the elastic damping layer 2 and the rigid layer 3, including the mass parameter, the rigidity parameter and the damping parameter, are determined according to the natural frequency of the elastic strip 1, so that the frequency of the vibration absorber is close to the natural frequency of the elastic strip, and the resonance of the elastic strip 1 is restrained. Designing a dynamic vibration absorber according to parameters of the dynamic vibration absorber aiming at omega-type elastic strips 1 and e-type elastic strips 1, wherein the dynamic vibration absorber comprises an elastic damping layer 2 and a rigid layer 3 as shown in figures 1-6; a first mounting hole for the elastic wall of the elastic strip 1 to pass through is formed in the center of the elastic damping layer 2, the inner diameter and the outer diameter of the elastic damping layer 2 are respectively 15 mm and 30mm, soft rubber is selected as a material, and the elastic modulus is 6 MPa; a second mounting hole for mounting the elastic damping layer 2 is formed in the center of the rigid layer 3, the inner diameter and the outer diameter of the rigid layer 3 are respectively 30mm and 45mm, and steel is selected as a material; the elastic damping layer 2 and the rigid layer 3 are connected through an adhesive to form a dynamic vibration absorption structure with the thickness of 10 mm.
In an alternative embodiment, the structure of the elastic damping layer 2 and the rigid layer 3 includes a circular ring shape-circular ring shape, circular ring shape-polygon shape, but is not limited to the above structural forms.
In an alternative embodiment, the elastic damping layer 2 and the elastic strip 1 are connected by means of an adhesive.
In an alternative embodiment, the steel density is 7850kg/m3。
The resonance response analysis is carried out on the elastic strip 1 with the dynamic vibration absorber, the acceleration frequency response function of the highest point of the elastic arm of the elastic strip 1 is calculated, and compared with the acceleration frequency response functions of the elastic strip of the original elastic strip and the elastic strip with the dynamic vibration absorber, as shown in fig. 7, as can be seen from fig. 7, the original elastic strip has obvious peak values at the first two-order natural frequencies of 520Hz and 600Hz, while the elastic strip 1 with the dynamic vibration absorber effectively inhibits the first two-order modes of the original elastic strip, and the amplitude value is obviously attenuated at the natural frequency. At the same time the elastic strip 1 with the dynamic vibration absorber shows a new peak at the frequency 419,720 Hz. The modal analysis shows that the first two-order natural frequencies of the elastic strip 1 with the dynamic vibration absorber are 419 Hz and 720Hz respectively, and the first two-order vibration modes still have vertical and longitudinal combined vibration with elastic arms in antisymmetry and symmetry. It can be seen that the elastic strip 1 with the dynamic vibration absorber changes the natural frequency of the elastic strip to a certain extent, so that the elastic strip can avoid the typical excitation frequency of the wheel track.
Based on a multi-degree-of-freedom system equivalent mass recognition method and a modal analysis result, the mass of the elastic strip additional dynamic vibration absorber is determined to be 0.14kg, the rigidity is determined to be 2.22kN/mm, the damping is determined to be 207N s/m, and the additional position is the highest point of the elastic arm. When the elastic strip 1 with the dynamic vibration absorber is normally installed, the buckling pressure is 9.4kN, and the maximum equivalent stress of the elastic strip 1 is 1330MPa, which is consistent with the original elastic strip. The resonance peaks of the elastic strip 1 of the additional vibration absorber at the original natural frequency of 520Hz and 600Hz are remarkably suppressed, and new peaks appear at 419 Hz and 720 Hz.
When the speed is 300km/h and the amplitude is 0.04mm, the maximum vertical acceleration values of the original elastic strip under the polygon of the 18-order wheel and the elastic strip with the dynamic vibration absorber are 2130 and 662m/s respectively2Vibration absorber with powerCompared with the original elastic strip, the elastic strip is reduced by 68.9 percent, and the maximum values of the stress amplitude are respectively 56MPa and 36 MPa; the maximum vertical acceleration values of original elastic strips and high-frequency elastic strips under the polygon of the lower wheel of the rail corrugation mill with the wavelength of 150mm are 3605 and 798m/s respectively2Compared with the original elastic strip, the elastic strip with the dynamic vibration absorber is reduced by 77.8 percent, and the maximum values of the stress amplitudes are 61MPa and 40MPa respectively. The elastic strip 1 with the dynamic vibration absorber vibrates to be far smaller than the original elastic strip on the whole level, the fatigue life of the elastic strip 1 with the dynamic vibration absorber is far longer than that of the original elastic strip, and the elastic strip 1 with the dynamic vibration absorber can not generate the phenomenon of resonance fatigue fracture under the working conditions of the existing wheel polygon and the rail corrugation.
It is to be understood that the above-described embodiments of the present invention are merely illustrative of or explaining the principles of the invention and are not to be construed as limiting the invention. Therefore, any modification, equivalent replacement, improvement and the like made without departing from the spirit and scope of the present invention should be included in the protection scope of the present invention. Further, it is intended that the appended claims cover all such variations and modifications as fall within the scope and boundaries of the appended claims or the equivalents of such scope and boundaries.
Claims (6)
1. The elastic strip dynamic vibration absorber is characterized by comprising an elastic damping layer (2) and a rigid layer (3); a first mounting hole for the elastic wall of the elastic strip (1) to pass through is formed in the center of the elastic damping layer (2), the inner diameter and the outer diameter of the elastic damping layer (2) are respectively 15 mm and 30mm, the material is soft rubber, and the elastic modulus is 6 MPa; a second mounting hole for mounting the elastic damping layer (2) is formed in the center of the rigid layer (3), the inner diameter and the outer diameter of the rigid layer (3) are respectively 30mm and 45mm, and steel is selected as a material; the elastic damping layer (2) and the rigid layer (3) are connected through an adhesive to form a dynamic vibration absorption structure with the thickness of 10 mm.
2. The elastic strip dynamic vibration absorber of claim 1, wherein the structure of the elastic damping layer (2) and the rigid layer (3) includes, but is not limited to, donut-donut, donut-polygon.
3. The elastic-strip dynamic vibration absorber according to claim 1, wherein the elastic damping layer (2) and the elastic strip (1) are connected by an adhesive.
4. The elastic strip dynamic vibration absorber of claim 1 wherein the steel material selected has a density of 7850kg/m3。
5. A parameter design method of a spring dynamic vibration absorber is characterized by comprising the following steps:
s1, dispersing the continuous structure of the fastener elastic strip into a non-coupling multi-freedom-degree model formed by combining a plurality of single-freedom-degree systems by adopting a modal analysis technology and according to the orthogonality of modal vectors, wherein the equivalent mass of the ith-order mode of the fastener elastic strip is as shown in a formula (1):
in the formula: miRepresenting the equivalent mass of the jth degree of freedom of the fastener elastic strip relative to the ith order mode; t istThe kinetic energy of the whole fastener elastic strip is obtained; (x)1,x2,···xj,···xN) The intrinsic vector represents the ith order mode of the fastener elastic strip; (m)1,m2,···mj,···mN) Is a discrete single degree of freedom mass; omegaiIs the ith order natural circle frequency;
s2, after the equivalent mass of the elastic strip is obtained, the equivalent rigidity of the elastic strip of the fastener in the ith-order mode can be obtained by the following formula (2):
and S3, obtaining the optimal parameters of the ith-order modal additional dynamic vibration absorber of the elastic strip of the fastener by utilizing a formula of the optimal harmony and optimal damping conditions of the single degree of freedom of the damping main system.
6. The method for designing parameters of the elastic strip dynamic vibration absorber according to claim 5, wherein the specific steps of S3 are as follows:
(1) calculate the mass of the fastener spring strip with dynamic vibration absorber, see formula (3)
mi＝μiMi (3)
(2) Calculating the optimal spring rate of the fastener elastic strip additional dynamic vibration absorber, see formula (4)
(3) Optimal damping coefficient of fastener elastic strip additional dynamic vibration absorber, see formula (5)
In the above formula,. mu.iIs the mass ratio; m isiRepresenting the mass of the fastener elastic strip ith-order modal dynamic vibration absorber; miRepresenting the i-th order modal equivalent mass of the fastener elastic strip; kiRepresenting the i-th order modal equivalent stiffness of the elastic strip of the fastener; k is a radical ofiRepresenting the optimal rigidity of the fastener elastic strip ith-order modal dynamic vibration absorber; c. CiRepresenting the optimal damping of the fastener elastic strip ith-order modal dynamic vibration absorber; ziRepresenting the ith order modal equivalent damping of the fastener elastic strip; zetaiThe i-th order modal equivalent damping ratio of the fastener elastic strip is shown.
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TW200301793A (en) * | 2001-11-30 | 2003-07-16 | Vossloh Werke Gmbh | Elastic element for clamping rails for rail vehicles |
| CN101093008A (en) * | 2007-07-18 | 2007-12-26 | 郑钢铁 | Composite damping material with interlayer being as metal rubber |
| CN108130827A (en) * | 2018-01-19 | 2018-06-08 | 北京欧得海大铁科技有限公司 | Fatigue crack-resistant ω type fastener high frequency springs |
| CN108277702A (en) * | 2018-02-06 | 2018-07-13 | 上海工程技术大学 | A kind of low stress high-damping railway fastening elastic rod |
-
2021
- 2021-04-12 CN CN202110388373.0A patent/CN113265911A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TW200301793A (en) * | 2001-11-30 | 2003-07-16 | Vossloh Werke Gmbh | Elastic element for clamping rails for rail vehicles |
| CN101093008A (en) * | 2007-07-18 | 2007-12-26 | 郑钢铁 | Composite damping material with interlayer being as metal rubber |
| CN108130827A (en) * | 2018-01-19 | 2018-06-08 | 北京欧得海大铁科技有限公司 | Fatigue crack-resistant ω type fastener high frequency springs |
| CN108277702A (en) * | 2018-02-06 | 2018-07-13 | 上海工程技术大学 | A kind of low stress high-damping railway fastening elastic rod |
Non-Patent Citations (1)
| Title |
|---|
| 张龙庆等: "动力吸振器在浮置板轨道低频振动控制中的应用", 《工程力学》, no. 09, 30 September 2016 (2016-09-30), pages 213 * |
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Application publication date: 20210817 |