CN106547946A - Non-linear vibrating system synchronizing characteristicss analysis method and device that shock electric machine drives - Google Patents
Non-linear vibrating system synchronizing characteristicss analysis method and device that shock electric machine drives Download PDFInfo
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Abstract
The present invention relates to the non-linear vibrating system synchronizing characteristicss analysis method and device of a kind of shock electric machine driving, wherein, methods described includes that the vibration system model driven according to asymmetric hysteresis resilience model and the reversed turning Double -motor excitation for pre-building sets up the non-linear vibrating system model of the soil compression vibrational system that the Double -motor excitation drives；The non-linear vibrating system model of the soil compression vibrational system driven according to the Double -motor excitation is analyzed to the run-in synchronism characteristic of the elemental body non-linear vibrating system.The kinetic model that the present invention is provided more is coincide with actual vibration compacting operating mode, thus can improve the accuracy of elemental body non-linear vibrating system run-in synchronism specificity analysises, can provide basis for follow-up further research.
Description
Technical field
The present invention relates to the Vibration Synchronization field in vibrating machine engineering, more particularly to the non-thread that a kind of shock electric machine drives
Property the analysis of vibrational system synchronizing characteristicss.
Background technology
Vibrating compacting is a kind of construction method being now widely used in road engineering and civil engineering, vibrating compacting system
System is to complete the most important equipment of this construction working, and vibrational energy is passed to by firming in the form of ripple by it using pendulum
Body, reduces the resistance of deformation of the soil body, increases its mobility, improves compaction and efficiency of compaction.
During compacting soil, the soil body can produce elastic deformation and larger to the Vibrating Compacting System that Double -motor excitation drives
Plastic deformation, the soil body due to only producing plastic deformation on direction vertically downward, so restoring force of the soil body to pendulum
The hysteretic loop formed between its displacement is asymmetric.It is this generally show in curves of stress-strain relationship it is not right
The characteristic of title is called asymmetrical hysteresis.When vibratory response of this asymmetrical hysteresis to system has a significant impact, palpus
Ensure that the run-in synchronism of many shock electric machines could realize system synchronization kinetic stability, and then ensure the workability of vibrating machine
Energy.
In the SELF-SYNCHRONOUS VIBRATION SYSTEM that Double -motor excitation drives, when the eccentric rotor on Double -motor excitation reaches synchronism stability
During operating, if off the power supply of a shock electric machine, can also make system realize that synchronism stability operates, but this is in nonlinear model
Can seldom realize in type (the particularly non-linear vibrating system containing hysteresis).Currently for shaking for one motor power of disconnection
The Double -motor excitation of dynamic system realizes synchronous operated analysis method, is only limitted to be analyzed by linear system, and in engineering
Most system is nonlinear system in practice, and its stability of synchronization analysis under powering-off state can seldom be realized, mainly
Reason is that the stability of synchronization interval of non-linear vibrating system is little, and operating mode is complicated, thus cannot realize the fortune of Vibrating Compacting System
Turn the accurate analysis of specificity analysises.
The content of the invention
Synchronous operated point is realized for the existing Double -motor excitation for the vibrational system for disconnecting a motor power
The defect that analysis is only carried out by linear system, the present invention propose the non-linear vibrating system synchronizing characteristicss that a kind of shock electric machine drives
Analysis method, including：
According to the vibration system that asymmetric hysteresis resilience model and the reversed turning Double -motor excitation for pre-building drive
System model sets up the non-linear vibrating system model of the soil compression vibrational system that the Double -motor excitation drives；
The non-linear vibrating system model of the soil compression vibrational system driven according to the Double -motor excitation is to the list
The run-in synchronism characteristic of plastid non-linear vibrating system is analyzed.
Alternatively, the relation and the phase between the Double -motor excitation and soil of the stress and strain according to soil
Interaction relation sets up the asymmetric hysteresis resilience model of soil, including：
Institute is set up according to the linear elastic stiffness of soil, the displacement of vibrational system, linear restoring power and nonlinear restoring force
State asymmetric hysteresis resilience model.
Alternatively, the asymmetric hysteresis resilience model of the soil is：
Wherein, a1, a2, a3For constant coefficient, y1、y2For the coordinate points in y-axis, and meet 0≤y1≤y2。
Alternatively, the non-linear vibrating system model of the soil compression vibrational system that the Double -motor excitation drives is：
Wherein, displacements of the y for the vertical direction of elemental body,For the speed of vertical direction,For the acceleration of vertical direction
Degree, quality of the m for plastid, which includes quality m of the quality of pendulum and two eccentric blocks1And m2, r1And r2For on shock electric machine
Eccentric block around revolution axle center radius,For the angular displacement of shock electric machine eccentric block,It is corresponding for eccentric block
The angular velocity in direction,For the angular acceleration of eccentric block respective direction, it is that c is linear damping, k is linear rigidity, c1, c2
For the gyrodaming of shock electric machine, Tm1, Tm2For the electromagnetic torque of shock electric machine, Tf1, Tf2For the load torque of shock electric machine.
Alternatively, the non-linear vibrating system mould of the soil compression vibrational system driven according to the Double -motor excitation
Type is analyzed to the run-in synchronism characteristic of the elemental body non-linear vibrating system, including：
In the case where the original state parameter of the Double -motor excitation has differences, wherein one shock electric machine is disconnected,
It is analyzed with the run-in synchronism characteristic to the elemental body non-linear vibrating system.
On the other hand, present invention also offers the non-linear vibrating system synchronizing characteristicss analysis that a kind of shock electric machine drives is filled
Put, including：
Non-linear vibrating system model sets up unit, for according to asymmetric hysteresis resilience model and pre-building
The vibration system model that reversed turning Double -motor excitation drives sets up the soil compression vibrational system that the Double -motor excitation drives
Kinetic model；
Service performance analytic unit, the kinetics of the soil compression vibrational system for being driven according to the Double -motor excitation
Model is analyzed to the run-in synchronism characteristic of the elemental body non-linear vibrating system.
Alternatively, the resilience model is set up unit and is further used for according to the linear elastic stiffness of soil, vibrational system
Displacement, linear restoring power and nonlinear restoring force set up the asymmetric hysteresis resilience model.
Alternatively, the asymmetric hysteresis resilience model of the soil is：
Wherein, a1, a2, a3For coefficient, y1、y2For the coordinate points in y-axis, and meet 0≤y1≤y2。
Alternatively, the non-linear vibrating system model of the soil compression vibrational system that the Double -motor excitation drives is：
Wherein, displacements of the y for the vertical direction of elemental body,For the speed of vertical direction,For the acceleration of vertical direction
Degree, quality of the m for plastid, which includes quality m of the quality of pendulum and two eccentric blocks1And m2, r1And r2For on shock electric machine
Eccentric block around revolution axle center radius,For the angular displacement of shock electric machine eccentric block,It is corresponding for eccentric block
The angular velocity in direction,For the angular acceleration of eccentric block respective direction, it is that c is linear damping, k is linear rigidity, c1, c2
For the gyrodaming of shock electric machine, Tm1, Tm2For the electromagnetic torque of shock electric machine, Tf1, Tf2For the load torque of shock electric machine.
Alternatively, the service performance analytic unit is further used for depositing in the original state parameter of the Double -motor excitation
In the case of difference, wherein one shock electric machine is disconnected, it is special with the run-in synchronism to the elemental body non-linear vibrating system
Property is analyzed.
Non-linear vibrating system synchronizing characteristicss analysis method and device that the shock electric machine of the present invention drives, according to asymmetric
The vibration system model that hysteresis resilience model and the reversed turning Double -motor excitation for pre-building drive sets up the bidifly
The non-linear vibrating system model of motor-driven soil compression vibrational system of shaking, further according to the soil that the Double -motor excitation drives
The model of nonlinear of earth compacting vibrational system is carried out to the run-in synchronism characteristic of the elemental body non-linear vibrating system point
Analysis, as the kinetic model and the actual vibration compacting operating mode that provide more are coincide, thus can improve elemental body Non-Linear Vibration
The accuracy of system synchronization service performance analysis, can provide basis for follow-up further research.
Description of the drawings
In order to be illustrated more clearly that the embodiment of the present invention or technical scheme of the prior art, below will be to embodiment or existing
Accompanying drawing to be used needed for having technology description is briefly described, it should be apparent that, drawings in the following description are the present invention
Some embodiments, for those of ordinary skill in the art, on the premise of not paying creative work, can be with basis
These accompanying drawings obtain other accompanying drawings.
Fig. 1 is the non-linear vibrating system synchronizing characteristicss analysis method of the shock electric machine driving of one embodiment of the invention
Schematic flow sheet；
Asymmetric hysteresis resilience model schematic diagrams of the Fig. 2 for the soil of one embodiment of the invention；
Mechanical model schematic diagrams of the Fig. 3 for the Vibrating Compacting System of one embodiment of the invention；
Structural representations of the Fig. 4 for the Double -motor excitation run-in synchronism specificity analysises device of one embodiment of the invention；
The rotating speed schematic diagram of Double -motor excitation when Fig. 5 is 3.14rad for the initial phase difference of one embodiment of the invention；
Double -motor excitation speed discrepancy schematic diagram when Fig. 6 is 3.14rad for the initial phase difference of one embodiment of the invention；
The phase contrast schematic diagram of Double -motor excitation when Fig. 7 is 3.14rad for the initial phase difference of one embodiment of the invention；
The phase plane schematic diagram of Double -motor excitation when Fig. 8 is 3.14rad for the first speed discrepancy of one embodiment of the invention.
Specific embodiment
To make purpose, technical scheme and the advantage of the embodiment of the present invention clearer, below in conjunction with the embodiment of the present invention
In accompanying drawing, the technical scheme in the embodiment of the present invention is explicitly described, it is clear that described embodiment be the present invention
A part of embodiment, rather than the embodiment of whole.Based on the embodiment in the present invention, those of ordinary skill in the art are not having
The every other embodiment obtained under the premise of making creative work, belongs to the scope of protection of the invention.
Fig. 1 is the non-linear vibrating system synchronizing characteristicss analysis method of the shock electric machine driving of one embodiment of the invention
Schematic flow sheet；As shown in figure 1, the method includes：
S1：According to the vibration that asymmetric hysteresis resilience model and the reversed turning Double -motor excitation for pre-building drive
System model sets up the non-linear vibrating system model of the soil compression vibrational system that the Double -motor excitation drives；
S2：The non-linear vibrating system model of the soil compression vibrational system driven according to the Double -motor excitation is to described
The run-in synchronism characteristic of elemental body non-linear vibrating system is analyzed.
Specifically, the non-linear vibrating system model of the soil compression vibrational system for being driven according to the Double -motor excitation exists
Run-in synchronism after system synchronization stable operation after one shock electric machine power supply of disconnection to the elemental body non-linear vibrating system
Characteristic is analyzed.
The non-linear vibrating system synchronizing characteristicss analysis method that the shock electric machine of the present embodiment drives, according to asymmetric hysteresis
The vibration system model that resilience model and the reversed turning Double -motor excitation that pre-builds drive is set up the bidifly and is shaken electricity
The non-linear vibrating system model of the soil compression vibrational system that machine drives, further according to the soil pressure that the Double -motor excitation drives
The non-linear vibrating system model of real vibrational system is carried out to the run-in synchronism characteristic of the elemental body non-linear vibrating system point
Analysis, as the kinetic model and the actual vibration compacting operating mode that provide more are coincide, thus can improve elemental body Non-Linear Vibration
The accuracy of system synchronization service performance analysis, can provide basis for follow-up further research.
Used as the preferred of the present embodiment, step S1 can include：
S11：Built according to the linear elastic stiffness of soil, the displacement of vibrational system, linear restoring power and nonlinear restoring force
Found the asymmetric hysteresis resilience model.
Specifically, Fig. 2 shows the asymmetric hysteresis resilience model of the soil of one embodiment of the invention, such as Fig. 2 institutes
Show, determined according to the interphase interaction of the relation and machine soil of soil stress and strain
Asymmetric hysteresis resilience model is：
Wherein, a1, a2, a3For coefficient, y1、y2For the coordinate points in y-axis, and meet 0≤y1≤y2。
Specifically, Fig. 3 shows the mechanical model of the Vibrating Compacting System of one embodiment of the invention, as shown in figure 3, root
According to the Practical Project problem of compacting soil, the mechanical model of soil compression vibrational system is established, the Double -motor excitation drives
The non-linear vibrating system model of soil compression vibrational system be：
Wherein, displacements of the y for the vertical direction of elemental body,For the speed of vertical direction,For the acceleration of vertical direction
Degree, quality of the m for plastid, which includes quality m of the quality of pendulum and two eccentric blocks1And m2, r1And r2For on shock electric machine
Eccentric block around revolution axle center radius,For the angular displacement of shock electric machine eccentric block,It is corresponding for eccentric block
The angular velocity in direction,For the angular acceleration of eccentric block respective direction, it is that c is linear damping, k is linear rigidity, c1, c2
For the gyrodaming of shock electric machine, Tm1, Tm2For the electromagnetic torque of shock electric machine, Tf1, Tf2For the load torque of shock electric machine.
Further, as the preferred of above-mentioned each method embodiment, driven according to the Double -motor excitation described in step S2
Run-in synchronism characteristic of the model of nonlinear of dynamic soil compression vibrational system to the elemental body non-linear vibrating system
It is analyzed, can includes：
S21：In the case where the original state parameter of the Double -motor excitation has differences, wherein one exciting electricity is disconnected
Machine, is analyzed with the run-in synchronism characteristic to the elemental body non-linear vibrating system.
Fig. 4 is the non-linear vibrating system synchronizing characteristicss analytical equipment of the shock electric machine driving of one embodiment of the invention
Structural representation；As shown in figure 4, described device includes：
Non-linear vibrating system model sets up unit 10, for according to the asymmetric hysteresis resilience model and in advance
The vibration system model that the reversed turning Double -motor excitation of foundation drives is set up the soil compression of the Double -motor excitation driving and is shaken
The non-linear vibrating system model of dynamic system；
Service performance analytic unit 20, the non-thread of the soil compression vibrational system for being driven according to the Double -motor excitation
Property model of vibration is analyzed to the run-in synchronism characteristic of the elemental body non-linear vibrating system.
Device described in the present embodiment can be used for performing said method embodiment, and its principle is similar with technique effect, this
Place repeats no more.
As the preferred of the present embodiment, non-linear vibrating system model set up unit 10 be further used for it is linear according to soil
Elastic stiffness, the displacement of vibrational system, linear restoring power and nonlinear restoring force set up the asymmetric hysteresis restoring force mould
Type.
Used as the preferred of the present embodiment, the asymmetric hysteresis resilience model of the soil is：
Wherein, a1, a2, a3For coefficient, y1、y2For the coordinate points in y-axis, and meet 0≤y1≤y2。
Further, as the preferred of the present embodiment, the soil compression vibrational system that the Double -motor excitation drives it is non-
Linear vibrating system model is：
Wherein, displacements of the y for the vertical direction of elemental body,For the speed of vertical direction,For the acceleration of vertical direction
Degree, quality of the m for plastid, which includes quality m of the quality of pendulum and two eccentric blocks1And m2, r1And r2For on shock electric machine
Eccentric block around revolution axle center radius,For the angular displacement of shock electric machine eccentric block,It is corresponding for eccentric block
The angular velocity in direction,For the angular acceleration of eccentric block respective direction, it is that c is linear damping, k is linear rigidity, c1, c2
For the gyrodaming of shock electric machine, Tm1, Tm2For the electromagnetic torque of shock electric machine, Tf1, Tf2For the load torque of shock electric machine.
Device described in the present embodiment can be used for performing said method embodiment, and its principle is similar with technique effect, this
Place repeats no more.
It should be noted that for device embodiment, due to itself and embodiment of the method basic simlarity, so description
Fairly simple, related part is illustrated referring to the part of embodiment of the method.
It is synchronous special to illustrate the non-linear vibrating system that the shock electric machine of the present invention drives with a specific embodiment below
Property analysis method and device, but do not limit protection scope of the present invention.
According to can determine that shown in Fig. 2 not on the basis of the asymmetric hysteretic behavior (referring to formula (1)) of above-mentioned foundation
Symmetrical hysteresis power f (y), hysteresis power analogous diagram are as shown in Figure 2.Based on formula (1)-(2), asymmetric hysteresis model of vibration is set up,
Simulation analysis are carried out according to model.Illustrate, parameter is as follows：M=78kg, m1=m2=3.5kg, r1=r2=0.08m, k
=1552000N/m, c=1000Nms/rad, J01=0.001kgm2, J02=0.01kgm2, c1=0.01Nms/
Rad, c2=0.01Nms/rad, select coefficient a1=40, a2=20, a3=40, y1=0.1, y2=0.2.Using exciting electricity
The excited frequency of machine rotor is 25Hz, when shock electric machine has differences rate (motor initial speed difference, initial phase difference),
Wherein one shock electric machine power supply is disconnected, the ruuning situation of rotating speed and phase place is analyzed.
Specifically, the power supply of a wherein shock electric machine behind 4 seconds of system operation, is disconnected, and in initial phase difference is
3.14rad, can obtain the rotating speed of Double -motor excitation as shown in figure 5, speed discrepancy is as shown in fig. 6, phase contrast is as shown in fig. 7, turn
The phase-plane diagram of speed difference and phase contrast is as shown in Figure 8.
Thus can draw, it is ensured that the power supply of shock electric machine 1 during Double -motor excitation there is some difference rate, was disconnected after 4 seconds
Afterwards, the rotating speed of Double -motor excitation and phase place keep synchronism stability operation.Rate (initial phase is had differences by arranging Double -motor excitation
Potential difference is different) in the case of, after 4 seconds, the shock electric machine 1 of deenergization obtains energy from the shock electric machine 2 of power supply, continue and
2 synchronism stability of shock electric machine runs, simply less than the rotating speed of stable operation before (as shown in Figure 5).By Double -motor excitation
Speed discrepancy and phase contrast figure (such as Fig. 6 and Fig. 7) understand, after 4 seconds, disconnect a shock electric machine power supply after, Double -motor excitation
Speed discrepancy and phase contrast all experienced big concussion after finally tend to synchronism stability, speed discrepancy is finally stable in 0 position, phase contrast
It is final stable more slightly smaller than π.There is a limit in the phase-plane diagram (such as Fig. 8) of the phase contrast and speed discrepancy of Double -motor excitation
Ring, phase plane path are all infinitely approached to limit cycle with helix shape, eventually arrive at limit cycle, and system is capable of achieving bidifly and shakes electricity
Machine phase contrast runs simultaneously, i.e., system remains to realize synchronism stability state.
The invention provides a class contains asymmetric Hysteretic nonlinearity vibration system model, ensureing Double -motor excitation presence
During difference, after disconnecting a shock electric machine power supply, remain to make shock electric machine realize run-in synchronism, realize dividing for system synchronization characteristic
Analysis method, as the kinetic model and the actual vibration compacting operating mode that provide more are coincide, thus it is non-linear to improve elemental body
The accuracy of vibrational system run-in synchronism specificity analysises, can provide basis for follow-up further research.
Above example is merely to illustrate technical scheme, rather than a limitation；Although with reference to the foregoing embodiments
The present invention has been described in detail, it will be understood by those within the art that：Which still can be to aforementioned each enforcement
Technical scheme described in example is modified, or carries out equivalent to which part technical characteristic；And these are changed or replace
Change, do not make the essence of appropriate technical solution depart from the spirit and scope of various embodiments of the present invention technical scheme.
Claims (10)
1. the non-linear vibrating system synchronizing characteristicss analysis method that a kind of shock electric machine drives, it is characterised in that include：
According to the vibrational system mould that asymmetric hysteresis resilience model and the reversed turning Double -motor excitation for pre-building drive
Type sets up the non-linear vibrating system model of the soil compression vibrational system that the Double -motor excitation drives；
The non-linear vibrating system model of the soil compression vibrational system driven according to the Double -motor excitation is to the elemental body
The run-in synchronism characteristic of non-linear vibrating system is analyzed.
2. method according to claim 1, it is characterised in that the relation of the stress and strain according to soil and institute
The asymmetric hysteresis resilience model that the interaction relationship between Double -motor excitation and soil sets up soil is stated, including：
According to the linear elastic stiffness of soil, the displacement of vibrational system, linear restoring power and nonlinear restoring force are set up not
Symmetrical hysteresis resilience model.
3. method according to claim 2, it is characterised in that the asymmetric hysteresis resilience model of the soil is：
Wherein, a1, a2, a3For coefficient, y1、y2For the coordinate points in y-axis, and meet 0≤y1≤y2。
4. method according to claim 3, it is characterised in that the soil compression vibrational system that the Double -motor excitation drives
Non-linear vibrating system model be：
Wherein, displacements of the y for the vertical direction of elemental body,For the speed of vertical direction,For the acceleration of vertical direction, m is
The quality of plastid, which includes quality m of the quality of pendulum and two eccentric blocks1And m2, r1And r2For the bias on shock electric machine
Radius of the block around revolution axle center,For the angular displacement of shock electric machine eccentric block,For eccentric block respective direction
Angular velocity,For the angular acceleration of eccentric block respective direction, c is linear damping, and k is linear rigidity, c1, c2For exciting electricity
The gyrodaming of machine, Tm1, Tm2For the electromagnetic torque of shock electric machine, Tf1, Tf2For the load torque of shock electric machine.
5. method according to claim 1, it is characterised in that the soil compression driven according to the Double -motor excitation
The non-linear vibrating system model of vibrational system is analyzed to the run-in synchronism characteristic of the elemental body non-linear vibrating system,
Including：
In the case where the original state parameter of the Double -motor excitation has differences, wherein one shock electric machine is disconnected, with right
The run-in synchronism characteristic of the elemental body non-linear vibrating system is analyzed.
6. the non-linear vibrating system synchronizing characteristicss analytical equipment that a kind of shock electric machine drives, it is characterised in that include：
Non-linear vibrating system model sets up unit, for according to asymmetric hysteresis resilience model and described in pre-building
The kinetic model of the soil compression vibrational system that Double -motor excitation drives；
Service performance analytic unit, the kinetic model of the soil compression vibrational system for being driven according to the Double -motor excitation
The run-in synchronism characteristic of the elemental body non-linear vibrating system is analyzed.
7. device according to claim 6, it is characterised in that the resilience model is set up unit and is further used for basis
The linear elastic stiffness of soil, the displacement of vibrational system, linear restoring power and nonlinear restoring force set up the asymmetric hysteresis
Resilience model.
8. device according to claim 7, it is characterised in that the asymmetric hysteresis resilience model of the soil is：
Wherein, a1, a2, a3For coefficient, y1、y2For the coordinate points in y-axis, and meet 0≤y1≤y2。
9. device according to claim 8, it is characterised in that the soil compression vibrational system that the Double -motor excitation drives
Non-linear vibrating system model be：
Wherein, displacements of the y for the vertical direction of elemental body,For the speed of vertical direction,For the acceleration of vertical direction, m is
The quality of plastid, which includes quality m of the quality of pendulum and two eccentric blocks1And m2, r1And r2For the bias on shock electric machine
Radius of the block around revolution axle center,For the angular displacement of shock electric machine eccentric block,For eccentric block respective direction
Angular velocity,For the angular acceleration of eccentric block respective direction, c is linear damping, and k is linear rigidity, c1, c2For exciting electricity
The gyrodaming of machine, Tm1, Tm2For the electromagnetic torque of shock electric machine, Tf1, Tf2For the load torque of shock electric machine.
10. device according to claim 6, it is characterised in that the service performance analytic unit is further used in institute
State Double -motor excitation original state parameter have differences in the case of, disconnect wherein one shock electric machine, with to the simple substance
The run-in synchronism characteristic of body non-linear vibrating system is analyzed.
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107194105A (en) * | 2017-06-07 | 2017-09-22 | 北京建筑大学 | A kind of Double -motor excitation synchronizing characteristics analysis method based on frequency catching |
| CN107330156A (en) * | 2017-06-07 | 2017-11-07 | 北京建筑大学 | Double -motor excitation synchronizing characteristics simulating analysis based on frequency catching |
| CN108334699A (en) * | 2018-02-05 | 2018-07-27 | 东北大学 | Bulk material analysis of flow characteristics method under a kind of non-linear uninstalling system of improved unilateral exciting |
| CN110108426A (en) * | 2019-05-05 | 2019-08-09 | 北京建筑大学 | A kind of double vibrating body vibrational systems and synchronizing characteristics analysis method |
| CN110119561A (en) * | 2019-05-05 | 2019-08-13 | 北京建筑大学 | A kind of list vibrating body vibrational system and synchronizing characteristics analysis method |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104809342A (en) * | 2015-04-23 | 2015-07-29 | 东北大学 | Parameter determination method of double-motor driven double-plastid self-synchronizing vibrating system |
-
2016
- 2016-09-30 CN CN201610876003.0A patent/CN106547946A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104809342A (en) * | 2015-04-23 | 2015-07-29 | 东北大学 | Parameter determination method of double-motor driven double-plastid self-synchronizing vibrating system |
Non-Patent Citations (1)
| Title |
|---|
| 李小号等: "非线性振动系统基于频率俘获现象的谐振同步分析", 《机械工程学报》 * |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107194105A (en) * | 2017-06-07 | 2017-09-22 | 北京建筑大学 | A kind of Double -motor excitation synchronizing characteristics analysis method based on frequency catching |
| CN107330156A (en) * | 2017-06-07 | 2017-11-07 | 北京建筑大学 | Double -motor excitation synchronizing characteristics simulating analysis based on frequency catching |
| CN108334699A (en) * | 2018-02-05 | 2018-07-27 | 东北大学 | Bulk material analysis of flow characteristics method under a kind of non-linear uninstalling system of improved unilateral exciting |
| CN110108426A (en) * | 2019-05-05 | 2019-08-09 | 北京建筑大学 | A kind of double vibrating body vibrational systems and synchronizing characteristics analysis method |
| CN110119561A (en) * | 2019-05-05 | 2019-08-13 | 北京建筑大学 | A kind of list vibrating body vibrational system and synchronizing characteristics analysis method |
| CN110119561B (en) * | 2019-05-05 | 2023-04-07 | 北京建筑大学 | Single-vibration-body vibration system and synchronous characteristic analysis method |
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