CN110309614A - A kind of synchronizer shift emulation mode - Google Patents
A kind of synchronizer shift emulation mode Download PDFInfo
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Abstract
The invention discloses a kind of synchronizer shift emulation modes, include the following steps: S1, establish synchronizer engaging process mechanical model, synchronizer engaging process mechanical model includes oil film pressure model, asperity contact pressure model, synchronous ring Bearing capacity model and synchronising torque model；S2, synchronizer engaging process Dynamics Simulation Model is established based on synchronizer engaging process mechanical model；S3, actual measurement primary data is obtained；S4, actual measurement primary data input synchronizer engaging process Dynamics Simulation Model is emulated.The present invention can effectively emulate the gear shifting force during shift, synchronising torque, the changing rules such as displacement, input speed of shifting gears, and the synchronization momentum emulation under various gears operating condition is smaller with test result error.
Description
Technical field
The present invention relates to simulation analysis technical field more particularly to a kind of synchronizer shift emulation modes.
Background technique
Synchronizer is as mechanical type manual speed-changer MT (Mechanical Transmission), mechanical automatic speed changing
Device AMT (Automatic Mechanical Transmission) and double-clutch automatic gearbox DCT (Dual Clutch
Transmission) key components and parts have an important influence the comfort of automobile, economy and shift performance.
So far from synchronizer invention, has certain research to it both at home and abroad.It include: to shift gears according to synchronizer synchronizing process
Power and shift change in displacement feature, are divided into eight zygophases for the course of work of synchronizer, and carry out to each stage
Detailed mechanics and Tribological Analysis；Heat analysis has been carried out to the friction surface of synchronous ring, has had studied the durability of synchronizer；It establishes
Synchronizer friction model has studied influence of the transmission oil to net synchronization capability；Have studied Synchromous device of gearbox failure procedure
With Analysis of Failure Mechanism；Synchronizer contact wear model is proposed, the influence that gear shifting force wears synchronizer is analyzed.To sum up institute
It states, mainly has studied the friction and failure mechanism of synchronizer both at home and abroad, and certain optimization has been carried out to synchronizer shift performance,
But synchronizer the whole series shifting system is not modeled, the Related Mathematical Models for mechanism of shifting gears are more fuzzy, and computational accuracy is not
It is high；To the simulation optimization of synchronizer, mostly single software cannot be accurately calculated.
Therefore, the simulation accuracy for how improving synchronizer shift, becomes those skilled in the art's urgent problem.
Summary of the invention
In conclusion the present invention needs the practical problem solved is how to improve the simulation accuracy of synchronizer shift.
To solve the above-mentioned problems, present invention employs the following technical solutions:
A kind of synchronizer shift emulation mode, includes the following steps:
S1, establish synchronizer engaging process mechanical model, synchronizer engaging process mechanical model include oil film pressure model,
Asperity contact pressure model, synchronous ring Bearing capacity model and synchronising torque model；
S2, synchronizer engaging process Dynamics Simulation Model is established based on synchronizer engaging process mechanical model；
S3, actual measurement primary data is obtained；
S4, actual measurement primary data input synchronizer engaging process Dynamics Simulation Model is emulated.
Preferably, oil film pressure model includes:
In formula, p indicates that oil film pressure suffered by synchronous ring, h indicate that synchronous ring and cone of friction czermak space, Φ indicate that synchronous ring rubs
Wipe material permeability, ΦxIndicate the pressure flow factor in synchronous ring width direction, x indicates synchronous ring width direction coordinate, η table
Show lubricating oil viscosity, d indicates that synchronous ring friction material thickness, t indicate synchronization time；
In formula, hoilThe oil film thickness that synchronous ring is indicated between two friction surface of conical ring that rubs, erf indicate error function, σ
Indicate that two friction surfaces combine roughness；
In formula, K=Φx(h3+ 12 Φ d), b indicates synchronous ring width,
Preferably, asperity contact pressure model includes:
In formula, pcIndicate asperity contact pressure, H indicates that film thickness ratio, λ indicate friction surface rough peak density, and β indicates micro-
Convex peak radius of curvature, σ indicate that two friction surfaces combine roughness, the secondary equivalent elasticity modulus of E ' expression friction, and A indicates nominal contact
Area；
In formula, E1,E2Respectively indicate the elasticity modulus of friction conical ring and synchronous ring, υ1,υ2Respectively indicate friction conical ring and same
Walk the Poisson's ratio of ring；
In formula,Indicate that friction surface summit height is equal toWhen film thickness than correlation function, φ*(s) friction is indicated
The Gaussian probability-density function of surface summit height, s indicate friction surface summit height.
Preferably, synchronous ring Bearing capacity model includes:
Ftotal=(1-B) Foil+BFc (7)
In formula, FtotalIndicate that synchronous ring bearing capacity, B indicate the ratio between asperity contact area and nominal contact area, Fc=
pcContact area；
In formula, 0≤B≤1 indicates that synchronous ring bearing capacity is all undertaken by oil film pressure as B=0, indicates as B=1
Synchronous ring bearing capacity is all undertaken by micro-bulge pressure；
In formula, r indicates synchronous ring mean radius, and α indicates friction cone angle；
In formula, FsleeveIndicate axial force suffered by clutch collar.
Preferably, synchronising torque model includes:
T=(1-B) Toil+BTc (12)
In formula, T indicates synchronising torque, ToilIndicate viscous torque, TcIndicate asperity contact friction torque；
In formula, ω indicates friction conical ring revolving speed, fcIndicate the coefficient of sliding friction, fc=0.13+0.008log (ω), log
The rotational speed difference logarithm that (ω) indicates synchronous ring between the conical ring that rubs；
In formula, I indicates synchronizer input terminal equivalent moment of inertia；
In conclusion including the following steps: S1 the invention discloses a kind of synchronizer shift emulation mode, establishing synchronization
Device engaging process mechanical model, synchronizer engaging process mechanical model include oil film pressure model, asperity contact pressure model,
Synchronous ring Bearing capacity model and synchronising torque model；S2, it synchronizer is established based on synchronizer engaging process mechanical model engaged
Journey Dynamics Simulation Model；S3, actual measurement primary data is obtained；S4, actual measurement primary data is inputted into synchronizer engaging process power
Simulation model is learned to be emulated.The present invention can be to the gear shifting force during shift, synchronising torque, shift displacement, input speed
Equal changing rules are effectively emulated, and the synchronization momentum emulation under various gears operating condition is smaller with test result error, and maximum is accidentally
Difference is 6.25%, minimal error 0.47%, and shift function emulates, worst error 9.10% preferable with test result consistency,
Minimal error is 0.29%.
Detailed description of the invention
In order to keep the purposes, technical schemes and advantages of invention clearer, the present invention is made into one below in conjunction with attached drawing
The detailed description of step, in which:
Fig. 1 is a kind of flow chart of synchronizer shift emulation mode disclosed by the invention；
Fig. 2 is the structural schematic diagram of lock ring type synchronized；
Fig. 3 is synchronizer shift process gear shifting force and shift displacement diagram；
Fig. 4 is sliding block stress diagram；
Fig. 5 is synchronous ring and cone of friction ring structure schematic diagram；
Fig. 6 is synchronizer friction model schematic diagram；
Fig. 7 is synchronizer Dynamic Co-Simulation model schematic；
Fig. 8 (a) and Fig. 8 (b) emulates shift process with built synchronizer Dynamic Co-Simulation model
Result schematic diagram；
Fig. 9 is the system structure diagram of confirmatory experiment in embodiment；
Figure 10 is gear shifting force and synchronising torque test simulation comparing result；
Figure 11 is shift displacement and input speed test simulation comparing result schematic diagram；
Figure 12 is synchronous momentum and shift function test simulation comparing result schematic diagram.
Specific embodiment
The present invention is described in further detail with reference to the accompanying drawing.
As shown in Figure 1, including the following steps: the invention discloses a kind of synchronizer shift emulation mode
S1, establish synchronizer engaging process mechanical model, synchronizer engaging process mechanical model include oil film pressure model,
Asperity contact pressure model, synchronous ring Bearing capacity model and synchronising torque model；
S2, synchronizer engaging process Dynamics Simulation Model is established based on synchronizer engaging process mechanical model；
Synchronizer engaging process Dynamics Simulation Model is constructed using Simulink and AMESim emulation platform, is used
It is the prior art that Simulink and AMESim emulation platform, which constructs simulation model, and details are not described herein.
S3, actual measurement primary data is obtained；
S4, actual measurement primary data input synchronizer engaging process Dynamics Simulation Model is emulated.
Inertia synchronizer is broadly divided into lock ring type and two kinds of lockpin-type, and present invention is generally directed to lock ring type synchronized, masters
It to be made of splined hub, clutch collar, gear ring to be joined, synchronous ring, friction conical ring, sliding block, pressure spring etc., as shown in Figure 2.
Synchronizer shift process, which can be mainly divided into, moves back gear, into gear, presynchronization, synchronization, ring, secondary pulse, gear
Switch, gear engagement etc. eight stages, as shown in figure 3, in Fig. 3 each stage be respectively as follows: 1 move back gear, 2 slidings, 3 presynchronization, 4 synchronizations, 5
Ring, 6 secondary pulses, 7 gear switches, the engagement of 8 gears.
The main function of synchronizer is to make speed changer input/output terminal revolving speed synchronous within a short period of time.Its presynchronization with
Synchronous phase synchronizer has an important influence net synchronization capability.In the presynchronization stage, clutch collar band movable slider axially moves.It is whole
A stage sliding block stress is as shown in figure 4, each stage is respectively as follows: 1 and moves back gear stage, 2 slip phases, 3 presynchronization stages, 4 same in Fig. 4
Step section.
As shown in figure 4, slip phase sliding block is started to axially move by axial force, presynchronization stage slipper push is synchronous
Ring continues to axially move to friction conical ring.Since synchronous ring and cone of friction interannular are there are lubricating oil, when synchronizing circumferential cone of friction
Viscous torque can be generated between two rings when ring is axially moved.Under viscous torque effect, synchronous ring is staggered half tooth, clutch collar
It is locked up.When gear shifting force further increases, sliding block locking positioning mechanism disequilibrium, be pressed into groove in clutch collar it
In.Sliding block axial force disappears at this time, and the presynchronization stage terminates.
Due to selector fork responsive to axial force, synchronous ring continues to axially move to friction conical ring synchronous phase, exist with
The lubricating oil of synchronous ring and cone of friction interannular is extruded to outside gap.In the process, due to two friction surface asperity contacts
Coarse friction torque and sticky shearing torque are produced with oil-shear.Under two kinds of torque collective effects, synchronizer input is defeated
Outlet realizes synchronization.
Therefore, the present invention is directed to synchronizer synchrone mechanism, establishes oil film pressure, asperity contact pressure, synchronous ring respectively
Four bearing capacity, synchronising torque models, and it is dynamic using Simulink and AMESim emulation platform building synchronizer engaging process
Mechanics Simulation model can analyze gear shifting force, the synchronising torque, shift displacement, the variation of input speed of synchronizer shift process
Rule.
When it is implemented, oil film pressure model includes:
In formula, p indicates that oil film pressure suffered by synchronous ring, h indicate that synchronous ring and cone of friction czermak space, Φ indicate that synchronous ring rubs
Wipe material permeability, ΦxIndicate the pressure flow factor in synchronous ring width direction, x indicates synchronous ring width direction coordinate, η table
Show lubricating oil viscosity, d indicates that synchronous ring friction material thickness, t indicate synchronization time；
In formula, hoilThe oil film thickness that synchronous ring is indicated between two friction surface of conical ring that rubs, erf indicate error function, σ
Indicate that two friction surfaces combine roughness；
In formula, K=Φx(h3+ 12 Φ d), b indicates synchronous ring width,
Synchronous ring and friction conical ring relatively rotate in synchronizing process, the axial force for acting on the engaging sleeve make synchronous ring with
Gap between friction conical ring constantly reduces, and the lubricating oil in gap is extruded or penetrates into cone of friction ring surface.According to synchronization
Ring and cone of friction ring structure feature and lubricating oil physical characteristic are it is found that the lubricant movement rule in gap meets Reynolds equation.
For the compressional movement of oil liquid between synchronous ring and the conical ring that rubs, establishes oil liquid extrusion mode two dimension in synchronizer synchronizing process and sit
Mark system, as Fig. 5 shows.
It is can be found that by the oil liquid analysis on change to synchronous ring and cone of friction interannular:
(1) oil liquid between synchronous ring and the conical ring that rubs is at axially symmetric distribution；
(2) circumferencial direction oil film thickness is a constant；
(3) two surface closing speeds are dh/dt.
In the case where considering pressure flow factor and material permeability, it is assumed that synchronous ring friction material is with a thickness of d.It synchronizes ring and rubs
The characteristics of motion of lubricating oil meets formula (1) between wiping conical ring, if synchronous ring and friction two rough surface peak heights of conical ring are all obeyed
The gaussian probability distribution that value is zero, then have formula (2), substitute into oil film pressure boundary condition, and acquiring oil film pressure is formula (3).
When it is implemented, asperity contact pressure model includes:
In formula, pcIndicate asperity contact pressure, H indicates that film thickness ratio, λ indicate friction surface rough peak density, and β indicates micro-
Convex peak radius of curvature, σ indicate that two friction surfaces combine roughness, the secondary equivalent elasticity modulus of E ' expression friction, and A indicates nominal contact
Area；
In formula, E1,E2Respectively indicate the elasticity modulus of friction conical ring and synchronous ring, υ1,υ2Respectively indicate friction conical ring and same
Walk the Poisson's ratio of ring；
In formula,Indicate that friction surface summit height is equal toWhen film thickness than correlation function, φ*(s) it indicates to rub
The Gaussian probability-density function of surface summit height is wiped, s indicates friction surface summit height.
If elastic-friction only occurs between synchronous ring and friction conical ring in synchronizing process, then rub secondary asperity contact pressure
For formula (4), in the present invention, it is assumed that synchronous ring friction material is copper-base powder metallurgy, cone of friction ring material is high-carbon steel；There is λ β
σ=0.05, σ/β=0.0113, E '=2.7 × 108Pa。
When it is implemented, synchronous ring Bearing capacity model includes:
Ftotal=(1-B) Foil+BFc (7)
In formula, FtotalIndicate that synchronous ring bearing capacity, B indicate the ratio between asperity contact area and nominal contact area, Fc=
pcContact area；
In formula, 0≤B≤1 indicates that synchronous ring bearing capacity is all undertaken by oil film pressure as B=0, indicates as B=1
Synchronous ring bearing capacity is all undertaken by micro-bulge pressure；
In formula, r indicates synchronous ring mean radius, and α indicates friction cone angle；
In formula, FsleeveIndicate axial force suffered by clutch collar.
Synchronous ring bearing capacity is carried jointly by oil film pressure and asperity contact in synchronizing process, therefore obtains formula (7), is led to
It crosses to synchronous ring force analysis it is found that synchronous ring bearing capacity FtotalEqual to axial force F suffered by clutch collarsleevesinα.Convolution
(4) and formula (9-12) can solve oil film change rate as formula (11).
When it is implemented, synchronising torque model includes:
T=(1-B) Toil+BTc (12)
In formula, T indicates synchronising torque, ToilIndicate viscous torque, TcIndicate asperity contact friction torque；
In formula, ω indicates friction conical ring revolving speed, fcIndicate the coefficient of sliding friction, fc=0.13+0.008log (ω), log
The rotational speed difference logarithm that (ω) indicates synchronous ring between the conical ring that rubs；
In formula, I indicates synchronizer input terminal equivalent moment of inertia；
Synchronising torque is mainly by viscous torque ToilWith asperity contact friction torque TcIt collectively constitutes, synchronising torque is
Formula (12), according to speed changer lifting rule, synchronizing torque is formula (15), and formula (13-15) substitution formula (12), which is arranged, can obtain formula
(16)。
In the present invention, synchronizer friction model is established using MATLAB/Simulink, as shown in Figure 6.Wherein AMESim-
Syn be AMESim model calling module, friction-torque be oil film thickness, rotational speed difference, synchronising torque (viscous torque with
Asperity contact friction torque) and ring Calculating Torque during Rotary module；
By the engagement gear ring revolving speed calculated in AMESim, synchronous ring revolving speed, synchronous annulate shaft to movement velocity, synchronous annulate shaft to
Axial force suffered by displacement, synchronous ring is input in Simulink model；According to the fluid model and asperity contact mould established
Type solves rotational speed difference and oil film thickness with 4 rank Runge-Kutta methods, and then finds out synchronising torque.It is finally that gained is synchronous
Torque is input in AMESim model, realizes AMESim and MATLAB/Simulink synchronization simulation.Simultaneously by MATLAB/
Ring torque calculated is input to AMESim model in Simulink module, accurately controls synchronizer shift process to realize
In ring process.
Synchronizer Dynamic Co-Simulation model is as shown in fig. 7, description of symbols in Fig. 7: the equivalent mould of 1 manual input
Type, 2 gear-shifting inhaul cables, 3 shift towers, 4 self-locking devices, 5 synchronizer monomers, 6 synchronizer input terminal equivalent models, 7 associative simulation moulds
Block, 8 differential mechanisms and whole vehicle model.As shown in fig. 7, its synchronizer physical model is built by mechanical structure module in AMESim, rub
It wipes model and solution is called by MATLAB/Simulink.Two model builts are opened simultaneously in simulation process, wherein AMESim model
Simulate synchronizer Machine Movement Process, MATLAB/Simulink model analyzing synchronizer friction process.Two model real-time perfoming numbers
According to interaction, data interaction time precision is 0.001s.
In the following, obtaining certain speed changer measured data, it is emulated using method disclosed in the present invention.Survey number
According to being as follows:
Initial value is input to built Dynamic Co-Simulation model, using 4Runge Kutta method to formula (11) and formula
(16) couple solution is carried out, synchronizes and calculates oil film thickness and rotational speed difference.To be calculated in AMESim the initial oil film thickness of gained and
Rotational speed difference is input in Simulink model, and will solve obtained oil film thickness and rotational speed difference every time as the first of next iteration
Initial value.Its differential equation iteration step length is 0.001, when rotational speed difference is less than 0.001r/min, is defaulted as synchronously completing.
Shift process is emulated with built synchronizer Dynamic Co-Simulation model, gear shifting force, synchronising torque,
Shift displacement and input speed simulation result such as Fig. 8 (a) and 8 (b) are shown.
By Fig. 8 (a) and Fig. 8 (b) it is found that model built can be to the gear shifting force during shift, synchronising torque, shift position
It moves, the changing rule of input speed is emulated.By Fig. 8 (a) it is found that model built gear shifting force simulation result can be to shifting gears
The stages such as gear, synchronization, secondary pulse, gear engagement of plucking in journey are simulated, and synchronising torque simulation result can embody synchronization
Device synchronizing process.By Fig. 8 (b) it is found that shift displacement has correlation with input speed variation tendency.It is inputted in synchronizing process
Revolving speed constantly reduces, and shift displacement remains unchanged.Model built can exchange gear shifting and be imitated with input speed changing rule
Very.
In the following, being tested to verify the validity of simulation result in the present invention using the system of such as Fig. 9.
Verification experimental verification has been carried out to model built.To ensure to emulate and test consistency, reference simulated conditions and synchronization
Operating condition of test is arranged in device actual working environment, and specific operating condition of test relevant parameter is as shown in the table.
Test and the gear shifting force in emulation, shift displacement, synchronising torque, the data such as input speed are extracted to compare point
Analysis, verifies the accuracy of model built.It is required according to test program, replaces gear shift between adjacent two grades, and acquire corresponding data.
The comparison of gear shifting force, synchronising torque, shift gears displacement, input terminal revolving speed and simulation analysis of 1 → 2 gear is measured respectively such as Figure 10, figure
Shown in 11.
As shown in Figure 10, model built can be able to carry out gear shifting force and synchronising torque and be effectively predicted.Gear shifting force test
As a result almost the same with simulation result variation tendency, but plucking gear, synchronization and secondary pulse stage, there are certain errors.It generates
The reason of this phenomenon, has: first is that because during the test, though the gear shifting force that shift laboratory technician by professional training, is applied
Still there is certain error in size.Second is that because system damping is missed with the damping of test system under test (SUT) in the presence of certain in model built
Difference.Model calculates synchronising torque test result and the changing rule of simulation result is almost the same, but due in model built
Coefficient of friction changing rule owes accurate, and is tested synchronizer and has only carried out running-in test, so trying in synchronous phase synchronising torque
It tests result and is slightly less than simulation result
By 11, it is found that model built is shifted gears, Displacement simulation result and test result variation are almost the same.Due to simulation model
There are certain errors with gap each in subjects, slightly have plucking gear, synchronization and secondary pulse stage gear-shifting ball joint position
Difference, therefore racking test of shifting gears has certain error with simulation result.Model built can be effectively predicted synchronizer input terminal and turn
Speed.Due to the influence of oil liquid resistance and air drag, synchronous phase input speed test result fall off rate is less than simulation result.
In gear engagement stage, since gear shifting force is greater than emulation gear shifting force during test, so test input turns after synchronously completing
Speed is slightly larger than simulation result
In order to further verify model built accuracy, various gears synchronizer in subject speed changer test
Card.For the accuracy of quantitative assessment model built, simulation result and test result are carried out using synchronous momentum and shift function
Quantitative analysis, result are as shown in figure 12.
As shown in Figure 12, the synchronization momentum of various gears synchronizer test result is more smaller than simulation result, this is because in reality
During border synchronizes device shift performance test, each rotary part of synchronizer receives transmission fluid damping effect.Low gear
The reason of synchronization momentum of position is greater than high tap position, generates this phenomenon is that the transmission of low gear interdigit is big, and synchronizer input/output terminal turns
Speed difference is big, and synchronization time extends.When carrying out dynamics simulation, secondary pulse is bound to occur in the certain situation of parameter, and
When synchronizing device shift performance test, the generation of secondary pulse is random, therefore the shift achievement of various gears simulation result is big
In test result.
For the error size of quantitative analysis model built, the test simulation result and test of synchronous momentum and function of shifting gears are tied
Fruit is for statistical analysis, and result is as shown in the table:
As seen from the above table, synchronous momentum emulates, worst error 6.25% smaller with test result error, and minimal error is
0.47%.The shift function and test result consistency of various gears simulation result are preferable, worst error 9.10%, and minimal error is
0.29%.The error amount of synchronous momentum and function of shifting gears is respectively less than 10%, therefore built Dynamics Simulation Model being capable of indicator synchronizer
Shift mechanism.
By the analysis to synchronizer shift process, oil film pressure, asperity contact pressure, synchronous ring bearing capacity are established
And four mathematical models of synchronising torque, Dynamics Simulation Model is established based on built mathematical model, and to model built into
Go verification experimental verification, the results showed that
(1) model built can change gear shifting force, synchronising torque, shift displacement, the input speed etc. during shift
Rule is effectively emulated.
(2) the synchronization momentum under various gears operating condition emulates, worst error 6.25% smaller with test result error, minimum
Error is 0.47%, and shift function emulates, worst error 9.10% preferable with test result consistency, minimal error 0.29%
Finally, it is stated that the above examples are only used to illustrate the technical scheme of the present invention and are not limiting, although passing through ginseng
According to the preferred embodiment of the present invention, invention has been described, it should be appreciated by those of ordinary skill in the art that can
To make various changes to it in the form and details, without departing from the present invention defined by the appended claims
Spirit and scope.
Claims (5)
- The emulation mode 1. a kind of synchronizer is shifted gears, which comprises the steps of:S1, synchronizer engaging process mechanical model is established, synchronizer engaging process mechanical model includes oil film pressure model, dimpling Body contact pressure model, synchronous ring Bearing capacity model and synchronising torque model；S2, synchronizer engaging process Dynamics Simulation Model is established based on synchronizer engaging process mechanical model；S3, actual measurement primary data is obtained；S4, actual measurement primary data input synchronizer engaging process Dynamics Simulation Model is emulated.
- The emulation mode 2. synchronizer as described in claim 1 is shifted gears, which is characterized in that oil film pressure model includes:In formula, p indicates that oil film pressure suffered by synchronous ring, h indicate that synchronous ring and cone of friction czermak space, Φ indicate synchronous ring friction material Expect permeability, ΦxIndicate the pressure flow factor in synchronous ring width direction, x indicates that synchronous ring width direction coordinate, η indicate profit Oil viscosity, d indicate that synchronous ring friction material thickness, t indicate synchronization time；In formula, hoilThe oil film thickness that synchronous ring is indicated between two friction surface of conical ring that rubs, erf indicate that error function, σ indicate Two friction surfaces combine roughness；In formula, K=Φx(h3+ 12 Φ d), b indicates synchronous ring width,
- The emulation mode 3. synchronizer as claimed in claim 2 is shifted gears, which is characterized in that asperity contact pressure model includes:In formula, pcIndicate asperity contact pressure, H indicates that film thickness ratio, λ indicate friction surface rough peak density, and β indicates dimpling peak Radius of curvature, σ indicate that two friction surfaces combine roughness, the secondary equivalent elasticity modulus of E ' expression friction, and A indicates nominal contact face Product；In formula, E1,E2Respectively indicate the elasticity modulus of friction conical ring and synchronous ring, υ1,υ2Respectively indicate friction conical ring and synchronous ring Poisson's ratio；In formula,Indicate that friction surface summit height is equal toWhen film thickness than correlation function, φ*(s) friction surface is indicated The Gaussian probability-density function of summit height, s indicate friction surface summit height.
- The emulation mode 4. synchronizer as claimed in claim 3 is shifted gears, which is characterized in that synchronizing ring Bearing capacity model includes:Ftotal=(1-B) Foil+BFc (7)In formula, FtotalIndicate that synchronous ring bearing capacity, B indicate the ratio between asperity contact area and nominal contact area, Fc=pcIt connects Contacting surface product；In formula, 0≤B≤1 indicates that synchronous ring bearing capacity is all undertaken by oil film pressure as B=0, indicates to synchronize as B=1 Ring bearing capacity is all undertaken by micro-bulge pressure；In formula, r indicates synchronous ring mean radius, and α indicates friction cone angle；In formula, FsleeveIndicate axial force suffered by clutch collar.
- The emulation mode 5. synchronizer as claimed in claim 4 is shifted gears, which is characterized in that synchronising torque model includes:T=(1-B) Toil+BTc (12)In formula, T indicates synchronising torque, ToilIndicate viscous torque, TcIndicate asperity contact friction torque；In formula, ω indicates friction conical ring revolving speed, fcIndicate the coefficient of sliding friction, fc=0.13+0.008log (ω), log (ω) table The rotational speed difference logarithm for showing synchronous ring between the conical ring that rubs；In formula, I indicates synchronizer input terminal equivalent moment of inertia；
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN113048230A (en) * | 2021-03-09 | 2021-06-29 | 中国矿业大学(北京) | AMT gear shifting process control method based on gear shifting sliding block abrasion prediction |
| CN113111449A (en) * | 2021-03-09 | 2021-07-13 | 西安法士特汽车传动有限公司 | Mechanical transmission static gear shifting simulation method based on AMESim |
| CN113404856A (en) * | 2021-06-24 | 2021-09-17 | 东风商用车有限公司 | Real-time monitoring method and monitoring device for service life of commercial vehicle synchronizer |
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| 张志刚等: "同步器同步机理建模与结构影响因素分析", 《哈尔滨工业大学学报》 * |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113048230A (en) * | 2021-03-09 | 2021-06-29 | 中国矿业大学(北京) | AMT gear shifting process control method based on gear shifting sliding block abrasion prediction |
| CN113111449A (en) * | 2021-03-09 | 2021-07-13 | 西安法士特汽车传动有限公司 | Mechanical transmission static gear shifting simulation method based on AMESim |
| CN113404856A (en) * | 2021-06-24 | 2021-09-17 | 东风商用车有限公司 | Real-time monitoring method and monitoring device for service life of commercial vehicle synchronizer |
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