CN111923936A - Quasi-zero stiffness vibration isolator for railway vehicle traction motor - Google Patents
Quasi-zero stiffness vibration isolator for railway vehicle traction motor Download PDFInfo
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- CN111923936A CN111923936A CN202010680369.7A CN202010680369A CN111923936A CN 111923936 A CN111923936 A CN 111923936A CN 202010680369 A CN202010680369 A CN 202010680369A CN 111923936 A CN111923936 A CN 111923936A
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- 230000001050 lubricating effect Effects 0.000 claims description 8
- 238000000034 method Methods 0.000 claims description 3
- 230000009286 beneficial effect Effects 0.000 abstract description 2
- 238000010586 diagram Methods 0.000 description 11
- 238000002955 isolation Methods 0.000 description 8
- 238000006073 displacement reaction Methods 0.000 description 7
- 239000006096 absorbing agent Substances 0.000 description 5
- 230000035939 shock Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 239000000725 suspension Substances 0.000 description 2
- 238000004364 calculation method Methods 0.000 description 1
- 239000008358 core component Substances 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 239000006185 dispersion Substances 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000011900 installation process Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012887 quadratic function Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61C—LOCOMOTIVES; MOTOR RAILCARS
- B61C3/00—Electric locomotives or railcars
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K5/00—Casings; Enclosures; Supports
- H02K5/24—Casings; Enclosures; Supports specially adapted for suppression or reduction of noise or vibrations
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- Engineering & Computer Science (AREA)
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- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention relates to a quasi-zero stiffness vibration isolator for a railway vehicle traction motor, which comprises a plurality of quasi-zero stiffness vibration isolators arranged above and at two sides of a frame cross beam of a vehicle body, wherein each quasi-zero stiffness vibration isolator is symmetrically arranged by taking the frame cross beam as the center, each quasi-zero stiffness vibration isolator is connected with a connecting support, the connecting support is rigidly connected with a motor support of the motor, each quasi-zero stiffness vibration isolator comprises a quasi-zero stiffness vibration isolator upper end mounting seat, a quasi-zero stiffness vibration isolator lower end mounting seat, a disc spring and a rubber spring, the disc spring is connected with the rubber spring in parallel, two ends of the disc spring and two ends of the rubber spring are respectively and fixedly connected with the quasi-zero stiffness vibration isolator upper end mounting seat and the quasi-zero stiffness vibration isolator lower end mounting seat, and the
Compared with the prior art, the invention is beneficial toReduce the vibration of the framework, improve the operation stability and the safety of the framework and the like.
Description
Technical Field
The invention relates to the technical field of railway vehicles, in particular to a quasi-zero stiffness vibration isolator for a traction motor of a railway vehicle.
Background
With the continuous development of railway vehicle technology, more and more people select subway or high-speed rail for traveling. At present, a subway or a high-speed rail mainly adopts a power dispersion technology, a driving motor is required to be mounted on a power bogie in a suspension mode, the driving motor is a core component of a driving system and is also one of vibration sources of the bogie, and the key problem of motor suspension is how to reasonably mount the driving motor on a framework and adopt proper vibration isolation measures to reduce the vibration of the framework. If the vibration isolation measures of the motor are not properly taken, the framework can vibrate too much, and the operation safety is threatened.
Disclosure of Invention
The invention aims to overcome the defects in the prior art and provide the quasi-zero stiffness vibration isolator for the traction motor of the railway vehicle, which aims at the vibration condition of the traction motor, reduces the vibration of a framework and improves the operation stability and safety of the framework.
The purpose of the invention can be realized by the following technical scheme:
the utility model provides a be used for quasi-zero rigidity isolator of rail vehicle traction motor, is including setting up a plurality of quasi-zero rigidity isolator in the top of the framework crossbeam of automobile body and both sides, and each quasi-zero rigidity isolator uses the framework crossbeam to be symmetrical arrangement as the center, and each quasi-zero rigidity isolator is connected with linking bridge, linking bridge and the motor support rigid connection of motor.
Quasi-zero stiffness vibration isolator includes quasi-zero stiffness vibration isolator upper end mount pad, quasi-zero stiffness vibration isolator lower extreme mount pad, belleville spring and rubber spring, quasi-zero stiffness vibration isolator upper end mount pad and linking bridge are connected, quasi-zero stiffness vibration isolator lower extreme mount pad is connected with the framework crossbeam of automobile body, belleville spring with rubber spring is parallelly connected, belleville spring's both ends rubber spring's both ends are connected with quasi-zero stiffness vibration isolator upper end mount pad, quasi-zero stiffness vibration isolator lower extreme mount pad respectively. The disc spring and the rubber spring are in parallel connection, and the rigidity of the vibration isolator is equal to the sum of the rigidity of the disc spring and the rubber spring.
Further, the ratio of the height to the thickness of the disc spring is larger than
And provides negative stiffness for the pre-compressed disc spring of the support surface during operation. The rubber spring is of a circular ring structure and provides positive rigidity in the working process.
Furthermore, the mounting seat at the lower end of the quasi-zero stiffness vibration isolator is connected with the framework cross beam through a mounting ring by adopting a bolt. The mounting ring and the mounting seat at the lower end of the quasi-zero stiffness vibration isolator are respectively connected with a connecting bracket.
Further, a lubricating layer is respectively arranged between the mounting ring and the connecting bracket and between the mounting seat at the lower end of the quasi-zero stiffness vibration isolator and the connecting bracket so as to release the transverse stiffness and the longitudinal stiffness of the vibration isolator.
Further, the mounting seat at the upper end of the quasi-zero stiffness vibration isolator is connected with the connecting support through a bolt.
Further, one or more quasi-zero stiffness vibration isolators are respectively arranged above and on two sides of the framework cross beam.
Further, the mounting ring is of a circular rigid structure.
The invention is used for the quasi-zero stiffness vibration isolator of the traction motor of the railway vehicle and has the working principle that:
the quasi-zero stiffness vibration isolator is designed by utilizing the negative stiffness characteristic of the disc spring and connecting the disc spring in parallel with the rubber spring, and is used for hanging a motor of a railway vehicle. The design steps are as follows: designing a rubber spring to ensure that the static deflection of the vertical stiffness of the rubber spring under a rated load state is equivalent to that of a common motor rubber shock absorber, and the effect of the rubber spring is the same as that of the common rubber shock absorber; then, designing parameters of height, thickness, inner diameter and outer diameter of the disc spring to enable the negative stiffness of the disc spring at the balance position in a rated bearing state to be superposed with the vertical stiffness of the rubber spring to obtain quasi-zero stiffness; and finally, designing an upper end mounting seat, a lower end mounting seat, a lubricating layer and a mounting ring of the quasi-zero stiffness vibration isolator, connecting the disc spring and the rubber spring in parallel, and releasing the transverse stiffness of the disc spring.
Compared with the prior art, the invention has the following beneficial effects:
(1) the structure form that a disc spring negative stiffness mechanism only providing negative stiffness is connected with a rubber spring in parallel is adopted, and the height-thickness ratio of the disc spring is larger than that of the disc spring
The quasi-zero stiffness vibration isolation system has the advantages that the rubber spring can obtain quasi-zero stiffness after the vertical stiffness and the negative stiffness of the disc spring are superposed, when the system vibrates in a small amplitude near the quasi-zero stiffness balance position, the vibration isolation initial frequency of the quasi-zero stiffness system is low, the vibration isolation frequency band is wide, and the vibration main frequency of the motor is usually more than 20 Hz;
(2) aiming at the vibration condition of a traction motor, quasi-zero stiffness vibration isolators are arranged above and at two sides of a framework cross beam of a vehicle body and structurally combined with the framework cross beam, so that the quasi-zero stiffness vibration isolators can be arranged in the transverse direction and the vertical direction when being installed;
(3) when the mounting ring and the mounting seat at the lower end of the vibration isolator are connected and mounted with the motor bracket, a lubricating layer is arranged in the middle of the mounting ring and the mounting seat, so that the transverse rigidity and the longitudinal rigidity of the quasi-zero rigidity vibration isolator can be released;
(4) the invention has simple and compact structure, convenient production and installation and good vibration isolation performance.
Drawings
FIG. 1 is a schematic structural diagram of a quasi-zero stiffness vibration isolator for a railway vehicle traction motor in an embodiment;
FIG. 2 is a schematic structural diagram of the quasi-zero stiffness vibration isolator in the embodiment;
FIG. 3 is a schematic structural view of a disc spring in an embodiment; wherein, fig. 3(a) is a cross-sectional front view structural diagram of the disc spring, and fig. 3(b) is a top view structural diagram of the disc spring;
FIG. 4 is a schematic structural diagram of a rubber spring in an embodiment, wherein FIG. 4(a) is a schematic structural diagram of a front view of the rubber spring, and FIG. 4(b) is a schematic structural diagram of a side view of the rubber spring;
FIG. 5 is a force characteristic curve diagram of a disc spring and a rubber spring in the embodiment;
figure 6 is a stiffness-displacement relationship diagram for the quasi-zero stiffness vibration isolator according to an embodiment;
the reference numbers in the figures indicate:
1. the device comprises a belleville spring, 2, a rubber spring, 3, a quasi-zero stiffness vibration isolator upper end mounting seat, 4, a quasi-zero stiffness vibration isolator lower end mounting seat, 5, a lubricating layer, 6, a mounting ring, 7, a framework cross beam, 8, a connecting support, 9, a motor support, 10 and a motor.
Detailed Description
The invention is described in detail below with reference to the figures and specific embodiments. It is to be understood that the embodiments described are only a few embodiments of the present invention, and not all embodiments. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, shall fall within the scope of protection of the present invention.
Examples
As shown in figure 1, the invention relates to a quasi-zero stiffness vibration isolator for a railway vehicle traction motor, which comprises a belleville spring 1, a rubber spring 2, an upper end mounting seat 3 of the quasi-zero stiffness vibration isolator, a lower end mounting seat 4 of the quasi-zero stiffness vibration isolator, a lubricating layer 5, a mounting ring 6, a framework cross beam 7, a connecting support 8, a motor support 9 and a motor 10.
The disc spring 1, the rubber spring 2, the upper end mounting seat 3 of the quasi-zero stiffness vibration isolator and the lower end mounting seat 4 of the quasi-zero stiffness vibration isolator form the quasi-zero stiffness vibration isolator. Specifically, two ends of a disc spring 1 are fixedly connected with an upper end mounting seat 3 of the quasi-zero stiffness vibration isolator and a lower end mounting seat 4 of the quasi-zero stiffness vibration isolator respectively, a rubber spring 2 is connected with the disc spring 1 in parallel, and two ends of the rubber spring 2 are fixedly connected with the upper end mounting seat 3 of the quasi-zero stiffness vibration isolator and the lower end mounting seat 4 of the quasi-zero stiffness vibration isolator respectively. Preferably, the upper end mounting seat 3 of the quasi-zero stiffness vibration isolator is fixedly connected with one end of an outer ring of the disc spring 1, and the lower end mounting seat 4 of the quasi-zero stiffness vibration isolator is fixedly connected with one end of an inner ring of the disc spring 1.
The disc spring 1 and the rubber spring 2 are in parallel connection, and the rigidity of the formed quasi-zero rigidity vibration isolator is equal to the sum of the rigidity of the disc spring and the rubber spring; the structure of the disc spring 1 is shown in FIG. 3, and its height/thickness ratio is larger than that of the disc spring
And is a pre-compressed disc spring, which provides negative stiffness during operation. The structure of the rubber spring 2 is shown in fig. 4, and is circular, and positive stiffness is provided during operation.
The mounting seat 3 at the upper end of the quasi-zero stiffness vibration isolator is connected with the connecting bracket 8 through a bolt. The connecting bracket 8 is rigidly connected with the motor bracket 9, and can adopt a bolt connection mode or a welding connection mode and the like. The lower end mounting seat 4 of the quasi-zero stiffness vibration isolator is connected with a framework cross beam 7 of the vehicle body through a mounting ring 6. The quasi-zero stiffness vibration isolators are arranged above and on two sides of the framework cross beam 7, and the quasi-zero stiffness vibration isolators are symmetrically arranged by taking the framework cross beam 7 as a center. The quasi-zero stiffness vibration isolators may be arranged in 1 or more number above and on both sides of the truss beam 7.
Specifically, the mounting seat 4 at the lower end of the quasi-zero stiffness vibration isolator is connected with a framework cross beam 7 through a mounting ring 6 by adopting a bolt. When the mounting ring 6, the mounting seat 4 at the lower end of the vibration isolator and the connecting bracket 8 are connected and mounted, the lubricating layer 5 is arranged in the middle of the mounting ring, the mounting seat and the connecting bracket to release the transverse and longitudinal rigidity of the vibration isolator. Preferably, the mounting ring 6 is a rigid structure in the shape of a circular ring.
The specific installation process of the quasi-zero stiffness vibration isolator for the traction motor of the railway vehicle in the embodiment is as follows:
the quasi-zero stiffness vibration isolator is designed by utilizing the negative stiffness characteristic of the disc spring 1 and connecting the disc spring 1 with the rubber spring 2 in parallel, and is used for hanging a railway vehicle motor. The design steps are as follows: the rubber spring 2 is designed, so that the static deflection of the vertical rigidity of the rubber spring in a rated bearing state is equivalent to that of a common motor rubber shock absorber, and the effect of the rubber spring is the same as that of the common rubber shock absorber; then, designing parameters of height, thickness, inner diameter and outer diameter of the disc spring 1 to enable the negative stiffness of the disc spring at the balance position to be superposed with the vertical stiffness of the rubber spring under a rated load state to obtain quasi-zero stiffness; and finally, designing an upper end mounting seat 3 of the quasi-zero stiffness vibration isolator, a lower end mounting seat 4 of the quasi-zero stiffness vibration isolator, a lubricating layer 5 and a mounting ring 6, connecting the disc spring 1 and the rubber spring 2 in parallel, and releasing the transverse stiffness of the disc spring 1.
In this embodiment, a disc spring without a supporting surface is used, and the schematic cross-sectional view is shown in fig. 3 (a). In the figure, tcIs a thickness, h0Is the initial height, D is the outer diameter and D is the inner diameter. The parameter design formula of the disc-shaped spring in the design step is as follows:
wherein E is the elastic modulus, mu is the Poisson's ratio, x is the displacement of the disc spring from the initial position in the vertical direction, and the parameter K1With respect to the ratio of outer to inner diameters C (C ═ D/D):
the principle that the disc spring has the characteristic of negative stiffness and the calculation is as follows:
the disk spring shows different stress characteristics according to different height-thickness ratios, and when the height-thickness ratio is larger than the thickness ratio
When the force is applied, a negative stiffness region (a region with a negative slope of the characteristic curve) appears.
In order to study the negative stiffness characteristic of the disc spring, the formula (1) is simplified and:
can be substituted by the formula (1)
The above formula is used for deriving x, and the stiffness expression of the disc spring is obtained as follows:
it can be seen that the stiffness k of the Belleville springdIs a quadratic function of the deformation x, with the axis of symmetry x ═ α tcAnd k isd(0)＝λ(α2+1)/tcIf the stiffness of the disc spring is more than 0, the requirement that delta is (-3 alpha) is met to ensure that the disc spring has a negative stiffness interval2-6(α2+1) > 0, i.e.
The interval of negative stiffness at this time is:
sub-diagram (a) of fig. 5 is a graph of disc spring force versus displacement, where there is a region with a negative stiffness characteristic (curvature is negative), which corresponds to the region of disc spring stiffness versus displacement curve of sub-diagram (a) of fig. 6 with negative stiffness (stiffness less than 0). And the negative stiffness is unstable in the vibration process, so the positive stiffness of the rubber spring is added as stiffness compensation, the force-displacement curve of the rubber spring is shown as a subgraph (b) in fig. 5, the disc spring and the rubber spring are in a parallel connection when being installed, the two forces are added to obtain a combined force-displacement curve as a subgraph (c) in fig. 5, the corresponding stiffness-displacement curve is shown as a subgraph (b) in fig. 6, the synthesized stiffness has no negative stiffness region, and the stiffness is equal to 0 at the equilibrium position (1.5 mm in the graph), namely the quasi-zero stiffness characteristic. For the quasi-zero stiffness vibration absorber installed on a bogie driving motor, when the system does small-amplitude vibration near the quasi-zero stiffness balance position, the vibration isolation starting frequency of the quasi-zero stiffness system is low, and the vibration isolation frequency band is wide, so that the vibration transmitted to a framework by the motor can be effectively isolated, the operation stability of the framework is improved, and the fatigue damage of the framework caused by overlarge motor excitation vibration is prevented.
While the invention has been described with reference to specific embodiments, the invention is not limited thereto, and those skilled in the art can easily conceive of various equivalent modifications or substitutions within the technical scope of the invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.
Claims (10)
1. The quasi-zero stiffness vibration isolator for the traction motor of the railway vehicle is characterized by comprising a plurality of quasi-zero stiffness vibration isolators arranged above and on two sides of a framework cross beam of a vehicle body, wherein each quasi-zero stiffness vibration isolator is symmetrically arranged by taking the framework cross beam as a center, and is connected with a connecting support, and the connecting support is rigidly connected with a motor support of the motor.
2. The quasi-zero stiffness vibration isolator for the traction motor of the railway vehicle as claimed in claim 1, wherein the quasi-zero stiffness vibration isolator comprises a quasi-zero stiffness vibration isolator upper end mounting seat, a quasi-zero stiffness vibration isolator lower end mounting seat, a disc spring and a rubber spring, the quasi-zero stiffness vibration isolator upper end mounting seat is connected with a connecting support, the quasi-zero stiffness vibration isolator lower end mounting seat is connected with a framework cross beam of a vehicle body, the disc spring is connected with the rubber spring in parallel, and two ends of the disc spring and two ends of the rubber spring are respectively connected with the quasi-zero stiffness vibration isolator upper end mounting seat and the quasi-zero stiffness vibration isolator lower end mounting seat.
3. The quasi-zero stiffness vibration isolator for railway vehicle traction motors of claim 1, wherein the disc springs are pre-compressed disc springs without bearing surfaces.
4. The method of claim 1The quasi-zero stiffness vibration isolator for the traction motor of the railway vehicle is characterized in that the height-to-thickness ratio of the disc spring is larger than that of the disc spring
5. The quasi-zero stiffness vibration isolator for railway vehicle traction motors of claim 1, wherein the rubber spring is circular ring shaped.
6. The quasi-zero stiffness vibration isolator for the traction motor of the railway vehicle as claimed in claim 2, wherein the lower end mounting seat of the quasi-zero stiffness vibration isolator is connected with the frame beam through a mounting ring by a bolt, and the mounting ring and the lower end mounting seat of the quasi-zero stiffness vibration isolator are respectively connected with the connecting bracket.
7. The quasi-zero stiffness vibration isolator for the traction motor of the railway vehicle as claimed in claim 6, wherein a lubricating layer is respectively arranged between the mounting ring and the connecting bracket and between the mounting seat at the lower end of the quasi-zero stiffness vibration isolator and the connecting bracket.
8. The quasi-zero stiffness vibration isolator for railway vehicle traction motors of claim 2, wherein the mounting seat at the upper end of the quasi-zero stiffness vibration isolator is connected with the connecting bracket through a bolt.
9. The quasi-zero stiffness vibration isolator for railway vehicle traction motors of claim 1, wherein one or more quasi-zero stiffness vibration isolators are respectively disposed above and on both sides of the frame cross beam.
10. The quasi-zero stiffness vibration isolator for railway vehicle traction motors of claim 6, wherein the mounting ring is a circular ring shaped rigid structure.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202010680369.7A CN111923936A (en) | 2020-07-15 | 2020-07-15 | Quasi-zero stiffness vibration isolator for railway vehicle traction motor |
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| CN202010680369.7A CN111923936A (en) | 2020-07-15 | 2020-07-15 | Quasi-zero stiffness vibration isolator for railway vehicle traction motor |
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| CN108599432A (en) * | 2018-05-11 | 2018-09-28 | 天津市金轮信德车业有限公司 | A kind of mounting structure of electric bicycle motor |
| CN109027085A (en) * | 2018-07-27 | 2018-12-18 | 同济大学 | A kind of low frequency vibration isolation device for bullet train floor |
| CN110439946A (en) * | 2019-07-30 | 2019-11-12 | 同济大学 | Equipment quasi-zero stiffness vibration isolators under a kind of railway vehicle truck |
-
2020
- 2020-07-15 CN CN202010680369.7A patent/CN111923936A/en active Pending
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH451305A (en) * | 1965-09-17 | 1968-05-15 | Licentia Gmbh | Resilient mounting of the stator housing of a large electrical machine with a vertical shaft and pulsating torque, in particular a single-phase alternator |
| US20070277797A1 (en) * | 2006-06-02 | 2007-12-06 | The University Of Houston System | Apparatus and method to pulverize rock using a superconducting electromagnetic linear motor |
| CN101055012A (en) * | 2007-05-15 | 2007-10-17 | 季馨 | Damp self-compensated ball-hinge type back/top frame vibration-isolator |
| CN101775842A (en) * | 2009-10-23 | 2010-07-14 | 上海路博橡胶减振器技术有限公司 | Three-dimensional shock absorbing support |
| CN101830230A (en) * | 2010-05-26 | 2010-09-15 | 湖南江麓冶金机械有限公司 | Electric trolley frequency conversion speed-regulating locomotive |
| CN102394548A (en) * | 2011-09-22 | 2012-03-28 | 北京航空航天大学 | Voice coil vibration isolating/vibration suppressing structure and control method thereof |
| CN107061615A (en) * | 2017-03-28 | 2017-08-18 | 同济大学 | It is a kind of to be used for the shock absorber that equipment is hung under railway vehicle truck |
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Application publication date: 20201113 |