CN208673333U - A kind of suspension type monorail vehicle Coupled Dynamics analogue system - Google Patents
A kind of suspension type monorail vehicle Coupled Dynamics analogue system Download PDFInfo
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- CN208673333U CN208673333U CN201820340541.2U CN201820340541U CN208673333U CN 208673333 U CN208673333 U CN 208673333U CN 201820340541 U CN201820340541 U CN 201820340541U CN 208673333 U CN208673333 U CN 208673333U
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Abstract
The utility model discloses a kind of suspension type monorail vehicle dynamics simulation systems, belong to technical field of rail traffic, its object is to be the existing suspension type monorail dynamics simulation device big technical problem of simulation result error when studying track girder local vibration of solution, by providing a kind of suspension type monorail vehicle system dynamics model, rubber wheel wheel track face contact mechanical model, the method for building up of track girder bottom plate and web equivalent face power applying method and vehicle and track girder Coupling Dynamic Model, construct the coupling dynamical simulation system of a kind of suspension type monorail vehicle and track girder, the utility model solve suspension type monorail Vehicular system suspension gear decoupling and it is equivalent, existing suspension type monorail kinetic model emulation simulation result error when studying track girder local vibration is big, it is difficult to extract track girder dynamic stress, dynamic strain result , can not accurate evaluation track girder local strength destroy etc. technical problems.
Description
Technical field
The utility model belongs to technical field of rail traffic, is related to a kind of suspension type monorail vehicle Coupled Dynamics emulation system
System.
Background technique
Suspension type monorail traffic is a kind of novel Rail Transit System, its strong, curve negotiating radius with climbing capacity
It is small, the advantages that low cost, low noise, the construction period is short, occupied area is few, it is able to satisfy short distance and the transport of the medium and small volume of the flow of passengers is appointed
Business.Suspension type monorail traffic is suitable for extension line, the connecting line of public traffic in metropolis time main line and backbone, and small and medium-sized cities are public
The main line of communication altogether, connecting line and the large-scale natural tourist attraction sightseeing on airport, high-speed rail, inter-city passenger rail station to downtown or scenic spot
The ranges such as the area Xian He connection wire.
Compared with traditional railway bridge, VIADUCTS IN URBAN RAIL TRANSIT, suspension type monorail traffic track beam section is small, track
Beam is vertical and lateral stiffness is lower, and the deformation of track girder caused by vehicle is big, so that the coupling power phase between vehicle and track girder
Interaction is stronger, and the vibration level of vehicle and track girder is likely to occur exceeded, and the long service performance of vehicle and track girder will be by
To large effect, therefore the dynamic interaction studied between suspension type monorail vehicle and track girder is of great significance.
In the research of high-speed railway vehicle bridge coupling vibration, usually by Vehicular system it is discrete by critical component form mostly just
System system, and the movement relation between each component is established based on dAlembert principle, Modular Bridge System usually regards euler beam or iron as
The wooden Xin Keliang, since euler beam or timoshenko beam have more mature theoretical formula, traditional Vehicular system and bridge
System can write the simulation analysis for realizing vehicle bridge coupling vibration in any programming software by program code.But for suspension
Formula monorail track beam, its underpart are hatch frame, cannot utilize euler beam or timoshenko beam simulated hanging formula monorail track beam,
Otherwise biggish calculating error or mistake can be introduced.In addition, each component movement relation of suspension type monorail Vehicular system model is more
Which component Vehicular system is equivalent to study its dynamic behavior be a technical problem, especially suspention beam machine by complexity
At home and abroad there is blank always in structure, the equivalent model for how constructing hanging beam mechanism.Therefore, it is difficult in existing programming software
The accurate coupling dynamic interaction simulation analysis realized between suspension type monorail vehicle and track girder.
For the dynamic interaction problem between vehicle and bridge, domestic and foreign scholars are mainly by establishing Vehicle-bridge System coupling
Kinetic model is closed to study it, due to the complexity of suspension type monorail vehicle and track beam structure, existing suspension
Formula single-track vehicle and the repercussion study of bridge power are rare, and minority scholar is based on general dynamic software both at home and abroad, establish outstanding
Hanging single-track vehicle system dynamics model, while using track girder as minor structure, by its quality, rigidity, mode and shape etc.
Information is imported into dynamics software, realizes straightway vehicle-bridge coupling power simulation analysis.But the above research method has one
It settles finally sex-limited, is imported into dynamics software by track girder minor structure, only by track girder low order or the main mould of former ranks
State information is imported into dynamics software, and track girder mode has missing in this process, affects calculating to a certain extent
Precision, particularly, suspension type monorail track girder is welded for steel plate, when wheel-rail interaction, track girder rail or walks
High vibration occurs for andante, and most local vibrations are high-frequency vibration, can not since above-mentioned model importing rank number of mode is limited
The vibration of real simulation track girder local high-frequency.
In addition, wheel and rail contact are thought of as single-point in the vehicle-bridge coupling analysis method of existing various traffic forms
Contact model, however suspension type monorail vehicle uses rubber wheel traveling, under train load effect, rubber wheel and track girder bottom plate
Or rail contact shape out of shape is being not single-contact, and contact area is mostly to have the approximate rectangular of certain area.Therefore, if
It will cause biggish calculating using single-contact model come the dynamic characteristics between simulated hanging formula single-track vehicle and track girder to miss
Difference, especially the vehicle bridge coupling vibration characteristic when calculating track girder local vibration, local stress and vehicle lintel and stitching.Therefore, it hangs
In hanging single track, it will consider more to meet reality at face contact between tire and track girder bottom plate or rail, but rubber wheel face connects
How touching wheel-rail model and face load are rationally applied to the research on track girder at home and abroad or blank.
Utility model content
The purpose of this utility model is that: to solve existing suspension type monorail dynamics simulation device in research track girder
Simulation result error big technical problem when local vibration provides a kind of suspension type monorail vehicle Coupled Dynamics analogue system.
The technical solution adopted in the utility model is as follows:
A kind of suspension type monorail vehicle Coupled Dynamics analogue system, including track girder, the steering being arranged in track girder
Frame, bogie arranged on left and right sides pass through directive wheel face contact model, the track girder of travelling wheel face contact model and track girder respectively
The track girder bottom plate connection of web, track girder；Bolster is provided in bogie, bolster arranged on left and right sides is outstanding by two systems respectively
It hangs the steering web of crossed strip-damper model, the vertical spring-damper model of secondary suspension and bogie, turn to bottom plate connection；
Bolster bottom surface is connected with centrepin, and the other end of centrepin is successively pierced by after bogie, track girder and is located at below track girder
Car body connection.
The analogue system is additionally provided with suspension gear model, and centrepin is connect by suspension gear model with car body.
The suspension gear model includes two groups of oblique pull spring models in "eight" shape mirror settings, left side oblique pull spring-loaded floating die
A point, the C point of type are connect on the left of centrepin bottom left, car body top respectively, B point, the D point minute of right side oblique pull spring model
It is not connect on the right side of centrepin bottom right, car body top；Pull rod sleeve, every group of drawing are arranged with outside every group of oblique pull spring model
Rod sleeve passes through the first elastic stop model close to one end of C point or D point and connect with car body top, centrepin bottom and car body
The first lateral damper equivalent model is also connected between top.
Directive wheel face contact model, travelling wheel face contact model, the secondary suspension crossed strip-damping mould of the analogue system
The vertical spring-damper model of type, secondary suspension includes the disposed in parallel second elastic stop model, second lateral damper etc.
Imitate model, the elastic stop model of the second of directive wheel face contact model, the both ends of the second lateral damper equivalent model and traveling
The elastic stop model of the second of wheel face contact model, the second lateral damper equivalent model both ends respectively with bogie, rail
The contact of road beam, secondary suspension crossed strip-damper model second elastic stop model, the second lateral damper equivalent model
Both ends with the second of the vertical spring-damper model of the secondary suspension elastic stop model, the second lateral damper equivalent model
Both ends are contacted with bolster, bogie respectively.
In conclusion by adopting the above-described technical solution, the beneficial effects of the utility model are:
The utility model provides a kind of suspension type monorail vehicle system dynamics model, rubber wheel wheel track face contact mechanics
The method for building up of model, track girder bottom plate equivalent face power applying method and vehicle and track girder Coupling Dynamic Model, building
On the one hand it is outstanding to solve suspension type monorail Vehicular system for a kind of coupling dynamical simulation system of suspension type monorail vehicle and track girder
The decoupling of loop wheel machine structure and the emulation of equivalent, existing suspension type monorail the kinetic model simulation result when studying track girder local vibration
Error is big, be difficult to extract track girder dynamic stress, dynamic strain result, can not accurate evaluation track girder local strength the technologies such as destroy and ask
Topic.
The utility model proposes the equivalent models of suspension type monorail hanging beam, and are established based on space coordinate conversion method
The movement relation of car body and suspension gear constructs one kind by 1 car body submodel, 2 bogie submodels, 2 suspention machines
21 freedom degree vehicle system dynamics models of structure submodel composition.
The utility model proposes finite element secondary development language is utilized, suspension type monorail is constructed in finite element software
Coupling dynamical simulation system between vehicle and guideway beam, and propose while there is the rubber for gathering non-linear and material nonlinearity
The equivalent method of face power in rubber tire wheel track face contact mechanical model and finite element model, can really and accurately simulating vehicle system
Vibration, track girder local vibration, track girder part dynamic stress and dynamic strain make emulation more close to truth, reduce rail
Phantom error when road beam local vibration.
The utility model realizes suspension type in same finite element software using the aobvious integral iteration algorithm implicitly mixed
The coupling dynamic characteristics research of single-track vehicle and guideway beam, can simulate simultaneously in track irregularity, seismic (seismal, random wind loads
Two system of vehicle under external world's excitation such as lotus and the coupled vibrations characteristic between guideway beam, expand the applicable model of the emulation mode
It encloses, makes emulation more close to truth, reduce phantom error when track girder local vibration.
Detailed description of the invention
Fig. 1 is the utility model centre mounted type single-track vehicle kinetic model end-view；
Fig. 2 is the emulation schematic diagram of car body and centrepin in the utility model；
Fig. 3 is suspension gear partial schematic diagram in the utility model；
Fig. 4 is the face contact front view that wheel is contacted with guideway beam rail level in the utility model；
Fig. 5 is the face contact side view that rubber wheel is contacted with guideway beam rail level in the utility model；
Fig. 6 is the rubber wheel face contact power equivalent method schematic diagram of the utility model middle orbit beam bridge rail level；
Fig. 7 is concentrated force equivalent nodal force schematic diagram in the utility model；
Fig. 8 is cubic spline difference bridge rail level displacement diagram in the utility model；
Fig. 9 suspension type monorail traffic scene test chart
Figure 10 is the emulation of car body Vertical Acceleration and actual measurement comparison diagram in the utility model；
Figure 11 is the emulation of cross-car vibration acceleration and actual measurement comparison diagram in the utility model；
Figure 12 is that the utility model middle orbit beam bridge span centre vertical deviation emulates and surveys comparison diagram；
When Figure 13 is that vehicle crosses curve in the utility model, car body mass center lateral shift displacement temporal response；
When Figure 14 is that vehicle crosses curve in the utility model, guideway beam traveling rail level part dynamic stress simulation result；
When Figure 15 is that vehicle crosses curve in the utility model, car body vertical acceleration frequency domain response simulation result；
When Figure 16 is that vehicle crosses curve in the utility model, car body vertical acceleration frequency domain response field actual measurement results；
Marked in the figure: 1, car body；2, bogie；3, bolster；4, centrepin；5, suspension gear model；6, track girder；7, two
It is hanging transverse spring-damper model；8, the vertical spring-damper model of secondary suspension；21, directive wheel face contact model；22, it walks
Row wheel face contact model；51, oblique pull spring model；52, lateral damper equivalent model；53, elastic stop model；54, oblique pull
Rod sleeve；61, track girder traveling rail level；62, running face finite element node；63, running face Eguivalent nodal loads；64, track girder
It is oriented to rail level.
Specific embodiment
In order to make the purpose of the utility model, technical solutions and advantages more clearly understood, below in conjunction with attached drawing and implementation
Example, the present invention will be further described in detail.It should be appreciated that specific embodiment described herein is only to explain this
Utility model is not used to limit the utility model.
Embodiment one
A kind of suspension type monorail vehicle Coupled Dynamics analogue system, the analogue system are mainly used for suspension type monorail vehicle
Carry out dynamics simulation.The analogue system includes track girder, and track girder includes track girder top plate, track web and track
Beam bottom plate, track web are arranged two groups, and two groups of one the first from left of track web are connected to left and right the two of track girder top plate rightly
Side forms " П " type structure after track girder top plate, the connection of track web.It is all provided on the inner sidewall of two groups of track webs
It is equipped with track girder bottom plate, two groups of track girder bottom plates are arranged in parallel with track girder top plate, and the sum of the width of two groups of track girder bottom plates
Less than the width of track girder top plate, thus spaced apart between the track girder bottom plate in left side and the track girder bottom plate on right side.
Bogie is additionally provided in track girder, bogie can shake in track girder.It is respectively set on left side, the right side of bogie
There are directive wheel face contact model, travelling wheel face contact model, directive wheel face contact model, travelling wheel face contact model are provided with
Two groups, a first from left is connected to the lower part of bogie left side, right side to two groups of directive wheel face contact models rightly respectively, and turns to
Frame is connected by the directive wheel face contact model of the right setting of a first from left and the track web of track girder；Two groups of travelling wheel face contacts
A first from left is connected on the left of bogie bottom surface, on the right side of bottom surface model rightly respectively, and bogie walking by the right setting of a first from left
The connection of the track girder bottom plate of row wheel face contact model and track girder.Pass through directive wheel face contact model, travelling wheel face contact model
Simulate movement of the directive wheel, travelling wheel on car body on track girder.Bolster is provided in bogie, bolster can be in bogie
Interior shaking.Secondary suspension crossed strip-damper model, the vertical bullet of secondary suspension are respectively arranged on left side, the right side of bolster
Spring-damper model, secondary suspension crossed strip-damper model, the vertical spring-damper model of secondary suspension are provided with two groups,
A first from left is connected to the lower part of bolster left side, right side to two groups of secondary suspension crossed strip-damper models rightly respectively, and shakes
Pillow is connect by secondary suspension crossed strip-damper model of the right setting of a first from left with the steering web of bogie left and right sides；Two
A first from left is connected on the left of bolster bottom surface, on the right side of bottom surface the group vertical spring-damper model of secondary suspension rightly respectively, and bolster is logical
The vertical spring-damper model of secondary suspension for crossing the right setting of a first from left is connect with the steering bottom plate of bogie left and right sides.In bolster
Bottom surface is connected with centrepin, and the other end of centrepin is successively pierced by the car body after bogie, track girder and being located at below track girder
Connection.
It, being capable of operation of the simulating vehicle on suspension type monorail track girder after using the above structure.
Embodiment two
On the basis of example 1, it is additionally provided with suspension gear model, which passes through suspension gear model and vehicle
Body is attached.
Embodiment three
On the basis of example 2, a kind of specific suspension gear model is provided.The suspension gear model is including being in
Two groups of oblique pull spring models of "eight" shape mirror settings, the A point of left side oblique pull spring model upper end, lower end C point respectively with
The left side connection in the left side of centrepin bottom, car body top, the B point of right side oblique pull spring model upper end, lower end D point respectively with
The right side connection on the right side, car body top of centrepin bottom.Pull rod sleeve, every group of drawing are arranged with outside every group of oblique pull spring model
Rod sleeve passes through the first elastic stop model close to one end of C point or D point and connect with car body top, centrepin bottom and car body
The first lateral damper equivalent model is also connected between top.The first lateral damper equivalent model perpendicular to centrepin with
Line setting between car body.
Example IV
On the basis of the above embodiments, the directive wheel face contact model, travelling wheel face contact model, secondary suspension are lateral
The vertical spring-damper model of spring-damper model, secondary suspension includes the disposed in parallel second elastic stop model, second
Lateral damper equivalent model, the elastic stop model of the second of directive wheel face contact model, the second lateral damper equivalent model
The second elastic stop model of both ends and travelling wheel face contact model, the both ends of the second lateral damper equivalent model distinguish
It is contacted with bogie, track girder, the elastic stop model of secondary suspension crossed strip-damper model second, the second lateral vibration absorbing
The both ends of device equivalent model and the second elastic stop model, the second lateral vibration absorbing with the vertical spring-damper model of secondary suspension
The both ends of device equivalent model are contacted with bolster, bogie respectively.
Embodiment five
The application provides a kind of suspension type monorail vehicle coupling power also directed to the Coupled Dynamics analogue system is mating
Emulation mode is learned, realizes the dynamics simulation to suspension type monorail vehicle.The emulation mode includes the following steps:
S1 constructs Coupled Dynamics analogue system, has including vehicle system dynamics model and guideway beam is established
Limit meta-model；
S2 sets integration step, and reads the track girder traveling rail level of Coupled Dynamics analogue system and be oriented to rail level
Random irregularities, seismic (seismal, track girder the RANDOM WIND load and Coupled Dynamics that are subjected to of Coupled Dynamics analogue system
The RANDOM WIND load that the Vehicular system of analogue system is subjected to；
S3, using the data read in step S2, in the vehicle dynamic model for presetting Coupled Dynamics analogue system
Each rubber wheel wheel track face contact power, and each rubber wheel wheel track face contact power is equivalent to discrete concentrfated load, and be applied to track
In beam kinetic model, power is carried out using track girder kinetic model of the implicit integration algorithm to Coupled Dynamics analogue system
Simulation calculation obtains the dynamics index response results of vehicle dynamic model.Wherein, the dynamics of the vehicle dynamic model
Index response results include the indexs such as dynamic deflection, vibration acceleration, dynamic stress, the dynamic strain of track girder；In addition, having one here
Point will define, and default rubber wheel wheel rail force only be needed in first integration step, since second step, rubber wheel wheel rail force is just
With the wheel rail force of calculating.
S4 is brought into using the data read in step S2 and by the dynamic deflection of the step S3 track girder being calculated
It is used in the vehicle system dynamics model of Coupled Dynamics analogue system, using quick display integral algorithm to Coupled Dynamics
The vehicle system dynamics model of analogue system is solved, and obtains the rubber wheel wheel track face contact in vehicle dynamic model
The dynamics indexs response results such as the vibration acceleration of power and each component, vibration velocity, vibration displacement；
S5, the dynamics index response of analysis each component of vehicle dynamic model and the dynamics index of track girder respond,
Judge whether vehicle begins computer capacity out；
S6, if vehicle ont yet goes out computer capacity, the rubber wheel wheel rail level in the vehicle dynamic model that step S5 is obtained
Contact force substitutes into step S3 as preset rubber wheel wheel track face contact power, carries out cycle calculations, analysis, judgement；If vehicle
Begin computer capacity out, this simulation is completed, recording simulation results.
Embodiment six
On the basis of embodiment five, Coupled Dynamics analogue system employed in step S1 is using embodiment one to reality
Apply the Coupled Dynamics analogue system in example four.I.e.: (i.e. including 1 car body submodel (i.e. car body), 2 bogie submodels
Bogie), 2 bolster submodels (i.e. bolster), 2 central pin models (i.e. centrepin), 2 hanging beam submodels (suspend in midair
Mechanism model), 4 secondary suspension submodels (i.e. secondary suspension crossed strip-damper models, the vertical spring-damper of secondary suspension
Model).Single bogie submodel includes that 4 travelling wheel submodels and 4 directive wheel submodels, bogie submodel are placed in rail
Inside road beam bridge finite element model, 4 travelling wheel submodels and guideway beam finite element model contacts baseplate, 4 directive wheels
Submodel is contacted with guideway beam finite element model web, and bogie submodel center has 2 two systems symmetrically arranged on the left and the right outstanding
Submodel is hung, bolster submodel is placed in secondary suspension submodel upper surface, and central pin model upper end is by articulated connection in shaking
Submodel is rested the head on, is connected between central pin model bottom end and car body submodel top by suspension gear submodel.
Due to the freedom degree that only one is turned about the Z axis between centrepin and bolster, by the two in tri- directions X, Y and Z
Translation regard a rigid body part as to study its motor behavior, centrepin and bolster combined mechanism are suspension gear, therefore outstanding
Hanging single-track vehicle vehicle by it is discrete be 1 car body, 2 bogies, 2 suspension gears totally 5 components form multi-rigid body system
System, it is vertical freedom degree Z respectively that wherein car body and each bogie, which simulate 5 freedom degrees, and laterally free degree Y sidewinders freedom
Spend φ, freedom degree of shaking the head ψ and nod freedom degree θ, ignore bolster and centrepin nod and yaw motion because it have it is smaller
Influence.Bolster and centrepin are considered as a rigid body, are modeled as 3 freedom degrees, are vertical freedom degree Z respectively, laterally free
Spend Y, roll freedom φ.The multi-rigid-body system of vehicle totally 21 freedom degrees.Secondary suspension submodel uses point contact spring damping
Unit simulation.
In order to rationally emulate the mechanical characteristic of car body and suspension gear, hanging beam mechanism need to be decoupled and be proposed corresponding equivalent
Model.The hanging beam mechanism submodel includes oblique pull spring submodel, sideway damper submodel and elastic stop submodel,
Brace submodel includes sleeve and oblique pull spring, and elastic stop submodel end thereof contacts are in roof, the other end and the sleeve
Hingedly.Oblique pull spring equivalent stiffness should meet K=EA/L, and wherein K is oblique pull spring equivalent stiffness, and E is suspension gear brace
The elasticity modulus of part material, A are the cross-sectional area of suspension gear brace, and L is the length of suspension gear oblique pull bar material.
Embodiment seven
On the basis of embodiment five or embodiment six, in the Coupled Dynamics analogue system, secondary suspension crossed strip-
The lateral force equation of damper model are as follows:
The longitudinal force equation of the vertical spring-damper model of secondary suspension are as follows:
The catenary motion equation of car body are as follows:
The equation of motion of nodding of car body are as follows:
The transverse movement equation of car body are as follows:
Car body sidewinders the equation of motion are as follows:
The yaw motion equation of car body are as follows:
The catenary motion equation of the community of centrepin and bolster composition are as follows:
The transverse movement equation of the community of centrepin and bolster composition are as follows:
The equation of motion is sidewindered in the community of centrepin and bolster composition are as follows:
The catenary motion equation of bogie:
The equation of motion of nodding of bogie:
The transverse movement equation of bogie:
Bogie sidewinders the equation of motion:
The yaw motion equation of bogie:
Wherein, Zci、Zti1、Zti2、Zhi1、Zhi2Respectively the i-th section vehicle car body vertical deviation, forecarriage vertical deviation, after
Vertical deviation is sold by bogie vertical deviation, preceding centrepin vertical deviation, rear center；Yci、Yti1、Yti2、Yhi1、Yhi2Respectively i-th
Save the displacement of vehicle cross-car, forecarriage lateral displacement, trailing bogie lateral displacement, preceding centrepin lateral displacement, rear center's pin
Lateral displacement；φci、φti1、φti2、φhi1、φhi2The respectively i-th section vehicle car body angle of roll, the forecarriage angle of roll, rear steering
The angle of roll is sold by the frame angle of roll, the preceding centrepin angle of roll, rear center；ψci、ψti1、ψti2Respectively the i-th section vehicle car body is shaken the head angle, forward
It shakes the head angle to frame, trailing bogie is shaken the head angle；βci、βti1、βti2The respectively i-th section vehicle car body point brilliance, the forecarriage point brilliance, after
The bogie point brilliance；Mc,Mh,MtThe respectively quality of car body, middle line pin and bolster, bogie；Icx,Icy,IczRespectively car body
Around the rotary inertia of X-axis, Y-axis and Z axis；Ihx,Ihy,IhzRespectively centrepin and bolster are used around the rotation of X axis, Y-axis and Z axis
Amount；Itx,Ity,ItzRespectively rotary inertia of the bogie around X-axis, Y-axis and Z axis；KzLij,KzRijRespectively indicate the i-th section vehicle j-th
Left and right air spring vertical stiffness on bogie；KzLij、KzRijRespectively indicate the left and right air on i-th j-th of bogie of section vehicle
Spring vertical stiffness；KyLij、KyRijRespectively indicate the left and right air spring lateral stiffness on i-th j-th of bogie of section vehicle；CzLij、
CzRijRespectively indicate the vertical damping of left and right air spring on i-th j-th of bogie of section vehicle；CyLij、CyRijRespectively indicate the i-th section
Left and right air spring on j-th of bogie of vehicle laterally damps；Kd、KgRespectively indicate the radial rigidity of travelling wheel and directive wheel；
FzLij、FzRijRespectively indicate the vertical force of the left and right air spring on i-th j-th of bogie of section vehicle；FyLij,FyRijIt respectively indicates
The cross force of left and right air spring on i-th j-th of bogie of section vehicle；FLij、FRijRespectively indicate i-th j-th of bogie of section vehicle
The pulling force of oblique pull the spring AC and BD of the suspension gear of lower section；PdLijk、 PdRijkIt respectively indicates on i-th j-th of bogie of section vehicle
K-th of wheel to the radial force of left and right wheel out of shape；PgLijk、PgRijkRespectively indicate k-th of wheel on i-th j-th of bogie of section vehicle
To the radial force of left and right directive wheel；FClijk,FCRijkK-th of the wheel respectively indicated on i-th j-th of bogie of section vehicle leads left and right
The lateral deviation power of travelling wheel； MClijk,MCRijkK-th of the wheel respectively indicated on i-th j-th of bogie of section vehicle leads travelling wheel to left and right
Aligning torque；FHijIndicate the lateral damper stress below i-th j-th of bogie of section vehicle；2Lc,2Lt,2LgBefore respectively indicating
Trailing bogie mass center fore-and-aft distance, bogie front and back travelling wheel is to directive wheel before and after spacing and bogie to spacing； 2l3,2l5Point
Not Biao Shi oblique pull spring CD and AB length；l1,l2Respectively indicate rubber metal pad to connecting rod CD and AB vertical distance；l0The company of expression
The vertical distance of bar AB to CD；A, b respectively indicate l2With l0Ratio and l1With l0Ratio；l4Indicate that car body mass center subtracts to lateral
The vertical distance of vibration device；l6Vertical distance of the expression car body mass center to rubber metal pad；l7Indicate centrepin mass center to lateral damper
Vertical distance；s1Vertical distance of the expression bogie mass center to tire centerline；2dw,2dsRespectively indicate bogie or so travelling wheel
Spacing and bogie or so secondary suspension horizontal spacing；Lh1,lh2Centrepin is respectively indicated to secondary suspension upper surface and arrives connecting rod
The vertical distance of AB；Hcb,HchCar body mass center is respectively indicated to the vertical distance of connecting rod CD and centrepin mass center to secondary suspension following table
The vertical distance in face；Hbt,HtwIt respectively indicates bogie mass center and arrives that secondary suspension lower surface is vertical and directive wheel center is vertical respectively
Position；θLij,θRijRespectively indicate connecting rod AC, CD respectively with reference axis YCReal-time angle；βLij, βRijRespectively indicate connecting rod AC
With the real-time angle and BD of connecting rod CD and the real-time angle of CD；χLij,χRijRespectively indicate the real-time angle of connecting rod AB Yu connecting rod AC
With the real-time angle of AB and BD；Rci,Rhij,RcijRespectively indicate car body, the sweep of centrepin and bogie；RciIndicate vehicle
The speed of service.
Embodiment eight
On the basis of embodiment five, embodiment six or embodiment seven, in order to effectively establish car body subsystem and centrepin
The movement relation of subsystem, proposes the method based on space coordinate conversion, establishes car body and centrepin respectively and bolster forms
Rigid body local coordinate system and using mass center as coordinate origin, xc,yc,zcFor using the geocentric coordinate system of car body as reference frame
Under coordinate value, xh,yh,zhFor the rigid body geocentric coordinate system that is formed using centrepin and bolster as reference frame under coordinate value,
X, y, z are the coordinate value under absolute coordinate system, are connected between car body and centrepin by suspension gear, by suspention beam brace
It is equivalent to oblique pull spring and sleeve, therefore this method can successfully decouple car body and centrepin, successfully realizes that dynamics is accurately asked
Solution, in simulation process, the local coordinate of each endpoint (A, B, C, D) of oblique pull spring AC and BD can be true at each moment
It is fixed, bullet finally can be acquired according to formula F=K Δ S in the hope of oblique pull spring AC and BD decrement by space coordinate shifting method
The pulling force of spring, wherein F is spring tension, and K is that oblique pull spring simulates rigidity, and Δ S is amount of spring compression, similarly inside suspension gear
The stress of lateral damper and elastic stop can be also determined, and finally can effectively be simulated between car body submodel and central pin model
Movement relation.
Wherein φc、φhRespectively indicate the angle of roll of car body subsystem and suspension gear, ψc、ψhIt respectively indicates car body and hangs
The angle of shaking the head of loop wheel machine structure.
Embodiment nine
On the basis of embodiment five, embodiment six, embodiment seven or embodiment eight, in Coupled Dynamics analogue system,
The wheel coordinate system of directive wheel, travelling wheel on car body (1) is defined as O1-X1Y1Z1, in X1-Z1Plane wheel tyre modeling
For along the spring damping model of the radially continuous distribution of entire tire, in Y1-Z1Plane, along coordinate Y1Direction, guide tyre power and is walked
Row tire force, which is regarded as, to be uniformly distributed, directive wheel, travelling wheel rubber tyre per unit width active force it is equal, entire rubber wheel
Wheel track face contact power is found out by down:
The same coordinate Y1When, it is being the tire compression deformation at x away from axle center displacement are as follows:
Δ Z (x)=[Zt-R(1-cosθ)-Zb-Z0(x)]/cosθ
The same coordinate Y1When, it can be expressed as away from axle center displacement for the tire local equivalents lateral pressure P (x) at x:
The total power of entire rubber wheel wheel track face contact power is closed P usable area point and is indicated are as follows:
Wherein, ZtFor tire centerline vertical deviation, ZbIt is displaced at tire x for bridge, Z0 (x) is the bridge at creeping of tyre x
Beam track irregularity, R are radius of wheel, and θ is radius and vertical direction angle, x at creeping of tyre x0For the level of tire centerline
Coordinate value, kz are model spring compression stiffness, and △ Z (x) is the tire compression displacement being displaced away from axle center be at x, czFor model resistance
Buddhist nun's coefficient,To be tire compression deformation rate at x away from axle center displacement；L is the length of tire interface rectangle；ΔZ(x)tTable
Show t moment away from the tire compression deformation that axle center displacement is at x, Δ Z (x)t-ΔtIndicate that (the t- Δ t) moment is at x away from axle center displacement
Tire compression deformation, b be tire model simulate when every section of tire unit width.
Embodiment ten
On the basis of embodiment five, embodiment six, embodiment seven, embodiment eight or embodiment nine, step S3 is by rubber
Take turns the equivalent method that non-linear face contact power is equivalent to discrete concentrfated load are as follows:
As shown in fig. 7, being carried out between concentrfated load is acted on two finite element nodes according to the fixed beam stress characteristic of beam-ends
It is equivalent:
Wherein PwIt (x) is discrete concentrfated load, Pw1(x) it is and concentrated force Pw(x) equal set of the adjacent posterior nodal point in position
Middle power, Pw2(x) it is and concentrated force Pw(x) the equivalent concentrated force of the adjacent front nodal point in position, Mw1(x) it is and concentrated force Pw(x) position
The equivalent moment of adjacent posterior nodal point, Mw2(x) it is and concentrated force Pw(x) equivalent moment of the adjacent front nodal point in position, a, b, l are respectively
Distance.
In addition, as shown in figure 8, the displacement of node similarly can only be also extracted, when equivalent in guideway beam finite element model
When concentrated force is between two nodes, in order to calculate rubber wheel active force, it is thus necessary to determine that each position of tire connects with track girder rail level
The displacement of the guideway beam rail level of contact, the present embodiment is using the position at finite element node two neighboring before and after cubic spline difference
Shifting obtains:
Zr=S1Z1+S2R1+S3Z2+S4R2
Wherein ZrFor the displacement of Wheel/Rail Contact Point, Z1And Z2It is limited that the adjacent front and back guideway beam in power contact point is distributed for wheel track
Meta-model modal displacement, S1, S2, S3, S4Cubic spline difference coefficient, a, l are respectively distance.
The above is only the preferred embodiment of the utility model only, is not intended to limit the utility model, all at this
Made any modifications, equivalent replacements, and improvements etc., should be included in the utility model within the spirit and principle of utility model
Protection scope within.
Claims (4)
1. a kind of suspension type monorail vehicle Coupled Dynamics analogue system, it is characterised in that: in-orbit including track girder (6), setting
Bogie (2) in road beam (6), bogie (2) arranged on left and right sides pass through directive wheel face contact model (21), travelling wheel respectively
Face contact model (22) is connect with the track girder bottom plate of the track web of track girder (6), track girder (6)；It is set in bogie (2)
It is equipped with bolster (3), bolster (3) arranged on left and right sides is hung down by secondary suspension crossed strip-damper model (7), secondary suspension respectively
It is connect to spring-damper model (8) with the steering web of bogie (2), steering bottom plate；Bolster (3) bottom surface is connected with centrepin
(4), the other end of centrepin (4) be successively pierced by bogie (2), track girder (6) afterwards be located at track girder (6) below car body
(1) it connects.
2. a kind of suspension type monorail vehicle Coupled Dynamics analogue system as described in claim 1, it is characterised in that: also set up
Have suspension gear model (5), centrepin (4) is connect by suspension gear model (5) with car body (1).
3. a kind of suspension type monorail vehicle Coupled Dynamics analogue system as claimed in claim 2, it is characterised in that: suspention machine
Structure model (5) includes two groups of oblique pull spring models (51) in "eight" shape mirror settings, the A of left side oblique pull spring model (51)
Point, C point are connect with centrepin (4) bottom left, car body (1) top left side respectively, B point, the D of right side oblique pull spring model (51)
Point is connect with centrepin (4) bottom right, car body (1) top right side respectively；Every group of oblique pull spring model (51) is arranged with outside
Pull rod sleeve (54), every group of pull rod sleeve (54) pass through the first elastic stop model (53) and vehicle close to one end of C point or D point
Connection at the top of body (1) is also connected with the first lateral damper equivalent model between centrepin (4) bottom and car body (1) top
(52)。
4. a kind of suspension type monorail vehicle Coupled Dynamics analogue system as described in claim 1, it is characterised in that: directive wheel
Face contact model (21), travelling wheel face contact model (22), secondary suspension crossed strip-damper model (7), secondary suspension are vertical
Spring-damper model (8) includes the disposed in parallel second elastic stop model, the second lateral damper equivalent model, guiding
The elastic stop model of the second of wheel face contact model (21), the both ends of the second lateral damper equivalent model and travelling wheel face contact
The elastic stop model of the second of model (22), the second lateral damper equivalent model both ends respectively with bogie (2), track
Beam (6) contact, the elastic stop model of secondary suspension crossed strip-damper model (7) second, the equivalent mould of the second lateral damper
The both ends of type and the second elastic stop model, the second lateral damper with the vertical spring-damper model of secondary suspension (8) are equivalent
The both ends of model are contacted with bolster (3), bogie (2) respectively.
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111597703A (en) * | 2020-05-11 | 2020-08-28 | 中国铁建重工集团股份有限公司 | Design parameter determination method and device for track inspection device and readable storage medium |
| CN112406910A (en) * | 2020-10-20 | 2021-02-26 | 中车长江车辆有限公司 | Suspension type rail transit system |
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2018
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111597703A (en) * | 2020-05-11 | 2020-08-28 | 中国铁建重工集团股份有限公司 | Design parameter determination method and device for track inspection device and readable storage medium |
| CN111597703B (en) * | 2020-05-11 | 2023-04-18 | 中国铁建重工集团股份有限公司 | Design parameter determination method and device for track detection device and readable storage medium |
| CN112406910A (en) * | 2020-10-20 | 2021-02-26 | 中车长江车辆有限公司 | Suspension type rail transit system |
| CN112406910B (en) * | 2020-10-20 | 2022-12-13 | 中车长江车辆有限公司 | Suspension type rail transit system |
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