CN103942362B - The method for designing of AMT hydraulic shifters - Google Patents

The method for designing of AMT hydraulic shifters Download PDF

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CN103942362B
CN103942362B CN201410105586.8A CN201410105586A CN103942362B CN 103942362 B CN103942362 B CN 103942362B CN 201410105586 A CN201410105586 A CN 201410105586A CN 103942362 B CN103942362 B CN 103942362B
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oil cylinder
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models
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CN103942362A (en
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陈慧岩
苗成生
刘海鸥
丁华荣
席军强
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Beijing Institute of Technology BIT
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Abstract

The present invention proposes a kind of method for designing of AMT hydraulic shifters.The AMT hydraulic shifters include oil cylinder, and methods described includes:CO models are built for the oil cylinder in the AMT hydraulic shifters, the CO models include system-level object function and three subsystems level object function;By iterative calculation, the optimal solution of the CO models is determined, wherein the dimensional parameters vector of optimal solution determination for needed for the oil cylinder;According to the dimensional parameters vector of the oil cylinder, the size of AMT hydraulic shifters is determined.The present invention obtains optimal solution by setting up CO models, and then selects cylinder sizes parameter according to optimal solution, completes the design of AMT hydraulic shifters.

Description

The method for designing of AMT hydraulic shifters
Technical field
The present invention relates to speed changer field, more particularly, it relates to AMT(Automated Manual Transmission, machine Tool formula automatic transmission)The method for designing of hydraulic shifter.
Background technology
AMT is widely used in recent years on heavy vehicles as one kind of automatic transmission.As realization certainly Move the important executive component of shelves manipulation, the bit selecting and extension shelves process of the gear-shifting actuating mechanism direct control transmission of AMT affect The dynamic property of vehicle, ride comfort, reliability.
Existing gear-shifting actuating mechanism is divided into fluid pressure type, pneumatic type and electrodynamic type substantially.On heavy vehicles, hydraulic pressure is performed Mechanism is most widely used.In the design to hydraulic shifter, bit selecting cylinder sizes and gear shifting oil cylinder size how are determined, It is the core of hydraulic shifter design.
The method for designing of existing hydraulic shifter, can be attributed to according to priori and single constraints, reference Mechanical engineering manual primary election dimensional parameters, then carry out the checking of other constraintss again.If being unsatisfactory for requiring, then select again Dimensional parameters are selected, until finding the dimensional parameters for meeting institute's Prescribed Properties.At least there is following three points defect in the existing method: (1)The result for obtaining is feasible solution, and non-optimal solution;(2)Multiple selection parameter is needed just to obtain the solution for needing, amount of calculation Greatly, computation burden can be increased significantly when constraints increases, and there is blindness;(3)Design and the small product size processed are big, High cost, efficiency are low.
The content of the invention
In order to overcome disadvantages described above, the present invention to propose a kind of method for designing of AMT hydraulic shifters, can solve the problem that existing There is problem of the acquired results for non-optimal solution in method.
On the one hand, a kind of method for designing of automatic mechanical transmission AMT hydraulic shifters, the AMT hydraulic shifts Mechanism includes oil cylinder, and methods described includes:Collaboration optimization CO models, institute are built for the oil cylinder in the AMT hydraulic shifters Stating CO models includes system-level object function and at least one subsystem irrespective of size object function;By iterative calculation, the CO is determined The optimal solution of model, wherein the dimensional parameters vector of optimal solution determination for needed for the oil cylinder;According to the oil cylinder Dimensional parameters vector, determines the size of the AMT hydraulic shifters.
Further, the oil cylinder in the AMT hydraulic shifters builds CO models, including:Build the oil The system goal function of cylinder;The subsystem objectives function of the oil cylinder is built, wherein the subsystem objectives function is the system The consistency constraint condition of system object function.
Further, the system goal function isThe subsystem objectives function ForWherein, l is the length of the oil cylinder, xiFor subsystem design variable:x1={d1, d2,d3,d4},x2={d1,d2,d3,d4},x3={d1,d2,d4, h }, zj *For element in the optimum results Z of system layer, xijFor i-th J-th design variable of subsystem, d1For the output end diameter of piston rod, d2For the internal diameter in the B chambers of oil cylinder, d3For in piston 0 Footpath, d4For the external diameter of the internal diameter or piston in the A chambers of oil cylinder, the casing wall thickness in the A chambers that h is oil cylinder.
Further, by iterative calculation, determine the optimal solution of the CO models, including:It is system-level to three subsystems Level distribution design vector desired value Z, the subsystems in the three subsystems level are before its own constraints is met Put, ask for its design variable and the system-level difference minimum of a value being supplied between the desired value of the subsystem respectively, and will be excellent Change result Xi(I=1,2,3)Return to system-level;System-level design vector X returned according to subsystem irrespective of sizeiReturn between construction subsystem Uniformity equality constraint, under its constraints, asks for the minimum of a value of system goal function, and optimum results Z ' is again passed to Subsystem irrespective of size;Successive ignition between system-level optimization and the optimization of subsystem irrespective of size, finally determines the optimum of the CO models Solution.
Further, the optimal solution for determining the CO models, including:According to about 0 beam condition of uniformity, it is determined that described The optimal solution of the system goal function of oil cylinder;According to load restraint condition, time constraint condition and strength constraint condition, institute is determined State the optimal solution of the subsystem objectives function of oil cylinder.
Further, it is described to determine the optimal solution of the system goal function of the oil cylinder according to consistency constraint condition, wrap Include:
Wherein, F (z) is the system goal function for needing optimization;diFor the design variable of system layer:d1For the defeated of piston rod Go out to hold diameter, d2For the internal diameter in the B chambers of oil cylinder, d3For the internal diameter of piston, d4For external diameter, the h of the internal diameter or piston in the A chambers of oil cylinder For the casing wall thickness in the A chambers of oil cylinder, l is the length of the oil cylinder, J1It is the consistency constraint of the first subsystem irrespective of size, J2It is second The consistency constraint of subsystem irrespective of size, J3It is the consistency constraint of the 3rd subsystem irrespective of size, d1i *For the optimum results of the first subsystem irrespective of size X1Middle element, d2i *For the optimum results X of the second subsystem irrespective of size2Middle element, d31 *、d32 *、d34 *、h3 *For the excellent of the 3rd subsystem irrespective of size Change result X3Middle element.
Alternatively, it is described according to load restraint condition, time constraint condition and strength constraint condition, determine the oil cylinder The optimal solution of subsystem objectives function, including:
According to load restraint condition, the optimal solution of the first subsystem objectives function of the oil cylinder is determined;
According to time constraint condition, the optimal solution of the second subsystem objectives function of the oil cylinder is determined;
According to strength constraint condition, the optimal solution of the 3rd subsystem objectives function of the oil cylinder is determined.
It is alternatively, described to determine the optimal solution of the first subsystem objectives function of the oil cylinder according to load restraint condition, Including:
Wherein, FmFor each the output of process active force of oil cylinder, m=1,2,3,4, FmSubscript 1,2 represent former and later two mistakes respectively Journey;SnFor the effective work area of corresponding process, n=1,2,3;P is oil sources principal pressure, is determined by system oil sources, is not belonging to AMT liquid The pressure controllable parameter of shifter itself, not in optimization range, output oil pressure is changing value P ∈ [4, a 4.5] Mpa, this tool Oil pressure minimum of a value is selected to calculate in body embodiment;P00 is taken as fuel tank oil pressure;FmaxFor maximum berth-changing strength 1700N.
It is alternatively, described to determine the optimal solution of the second subsystem objectives function of the oil cylinder according to time constraint condition, Including:
Wherein, Pɑ、PbThe oil pressure in hydraulic cylinder A, B chambers is represented respectively, and subscript 1,2 represents former and later two working stages respectively;tj Represent the shift time of four gear shift strokes.
It is alternatively, described to determine the optimal solution of the 3rd subsystem objectives function of the oil cylinder according to strength constraint condition, Including:
Wherein, δ is casing wall thickness allowable;F represents the maximum tension stress of piston rod;d0For in the end thread of piston rod Footpath, d0=d1- 1.0825e, e are pitch;σnRepresent the combined stress at the dangerouse cross-section of piston rod;[σ] is allowable stress, [σ]= σs/n2, σsFor screw thread yield point, n2For safety coefficient.
The present invention is by setting up CO(Collaborative Optimization, collaboration optimization)Model obtains optimal solution, And then cylinder sizes parameter is selected according to optimal solution, complete the design of AMT hydraulic shifters.
Additionally, the method according to the invention does not have blindness, computational efficiency can be improved, the work of oil cylinder is favorably improved Make efficiency, reduce volume and cost.
Description of the drawings
In order to be illustrated more clearly that the technical scheme of the embodiment of the present invention, below will be to making needed for the embodiment of the present invention Accompanying drawing is briefly described, it should be apparent that, drawings described below is only some embodiments of the present invention, for For those of ordinary skill in the art, on the premise of not paying creative work, can be obtaining other according to these accompanying drawings Accompanying drawing.
Fig. 1 shows the gear arrangement of nine grades of AMT of heavy vehicle.
Structural representations of the Fig. 2 for AMT.
Structural representations of the Fig. 3 for the hydraulic shifter of AMT.
Structure diagrams of the Fig. 4 for the gear shifting oil cylinder of AMT.
CO models of the Fig. 5 for gear shifting oil cylinder.
Specific embodiment
Below in conjunction with the accompanying drawing in the embodiment of the present invention, the technical scheme in the embodiment of the present invention is carried out clear, complete Site preparation is described, it is clear that described embodiment is a part of embodiment of the present invention, rather than whole embodiments.Based on this Embodiment in bright, the every other reality obtained on the premise of creative work is not made by those of ordinary skill in the art Example is applied, should all belong to the scope of protection of the invention.
The method for designing of the AMT hydraulic shifters of the present invention, including three below step.
Step one, is the oil cylinder in AMT hydraulic shifters(For example, shift cylinder and/or bit selecting oil cylinder)Build CO moulds Type, the CO models can include system-level object function and three subsystems level object function.
It is, building the system goal function of the oil cylinder;Build the subsystem objectives function of the oil cylinder, wherein institute State the consistency constraint condition that subsystem objectives function is the system goal function.
Step 2, by iterative calculation, determines the optimal solution of the CO models, wherein the optimal solution is the oil cylinder The dimensional parameters vector of required determination.
It is, it is system-level to three subsystems level distribution design vector desired value Z, it is each in the three subsystems level Individual subsystem is asked for its design variable on the premise of its own constraints is met, respectively and is supplied to the subsystem with system-level Desired value between difference minimum of a value, and by optimum results Xi(I=1,2,3)Return to it is system-level, wherein;System-level basis The optimum results X that the three subsystems level is returnediConstruction subsystem between consistency constraint, under its constraints, ask for be The minimum of a value of system object function, and optimum results Z ' is again passed to subsystem irrespective of size as new design vector desired value;Through Successive ignition between system-level optimization and the optimization of subsystem irrespective of size, finally determines the optimal solution of the CO models.
Wherein, according to consistency constraint condition, determine the optimal solution of the system goal function of the oil cylinder;According to load about Beam condition, time constraint condition and strength constraint condition, determine the optimal solution of the subsystem objectives function of the oil cylinder.
Step 3, according to the dimensional parameters vector of the oil cylinder, determines the size of the AMT hydraulic shifters.
In a specific embodiment, with nine grades of automatic mechanical transmission 5S-111GP of heavy vehicle(Climb a grade C, 1~8 Shelves and reverse gear R)As a example by, its gear arrangement is as shown in Figure 1.The AMT is made up of main tank and odd-side, as shown in Figure 2.Main tank is three axles Formula fixed axis gear gearbox, realize 1/5,2/6,3/7,4/8, reverse gear and climb the switching of six gears of shelves.Odd-side is planetary gear Gearbox, realizes the switching of two gears of high and low shift.Realize in main tank each gear switching be by selector shaft realize, Manipulate selector shaft rotation to be capable of achieving to hang(Pluck)Shelves, manipulate selector shaft axially-movable and are capable of achieving bit selecting.By two electromagnetic gas valves Control, the switching of high and low shift is realized in odd-side.Due to AMT simple structures, here is not described in detail.
The hydraulic shifter of AMT is main tank shifter, mainly includes bit selecting oil cylinder 1, gear shifting oil cylinder 2, static housing 3 With corresponding connector, as shown in Figure 3.Bit selecting oil cylinder 1 and gear shifting oil cylinder 2 control respectively the selector shaft of AMT main tanks axial direction and Rotary motion, realizes bit selecting and gear-change operation.Wherein, the piston rod of bit selecting oil cylinder 1 is directly connected with the selector shaft 4 of AMT main tanks, Its axially-movable is controlled, realizes that bit selecting is operated;Gear shifting oil cylinder 2 is connected with the selector shaft 4 by swing arm, Jing swing arms conversion, will be living The transform linear motion of stopper rod is the rotary motion of the selector shaft 4 of AMT main tanks, realizes gear-change operation.
Here, bit selecting oil cylinder 1 and gear shifting oil cylinder 2 are three oil cylinders, by two groups of two-position three way high-speed switch electromagnetic valves(Example Such as, one group is bit selecting magnetic valve HSV1And HSV2, another group is gear-shifting solenoid valve HSV3And HSV4)Control cylinder two ends oil pocket Fluid charge and discharge, realizes the motion of three positions of piston rod, and as shown in table 1, wherein N is sky to each gear magnetic valve action logic Shelves.
1 magnetic valve action logic table of table
AMT hydraulic shifters are directly mounted on the casing of AMT main tanks by selector shaft 4, thus belong to the outside of AMT Additional component.As vehicle allows installing space limited, therefore it is required that the appearance and size of the AMT hydraulic shifters is as far as possible little, Matching to strengthen its practicality and with dynamical system.
The topmost part of AMT hydraulic shifters is bit selecting oil cylinder 1 and gear shifting oil cylinder 2.Bit selecting oil cylinder 1 and gear shift Oil cylinder 2 not only determines the volume size of AMT hydraulic shifters, also directly manipulates gearshift procedure, affects AMT hydraulic shift machines The ride comfort and dynamic property of structure, and the service life of bit selecting oil cylinder 1 and gear shifting oil cylinder 2 by determine AMT hydraulic shifters can By property.
As bit selecting oil cylinder 1 is identical with the version of gear shifting oil cylinder 2, simply dimensional parameters are different.In order to Simplify explanation, only will describe how physical dimension is determined by the method for the present invention by taking gear shifting oil cylinder 2 as an example in detail below.
Structure diagrams of the Fig. 4 for gear shifting oil cylinder 2.As illustrated, gear shifting oil cylinder 2 is main by piston rod 21(End processes spiral shell Line), piston 22, cylinder body 23, cylinder cap 24 constitute.Gear shifting oil cylinder 2 includes A chambers and B chambers Liang Ge chambers, high-speed switch valve HSV3, HSV4 Control A, B chamber respectively enters fuel-displaced.
Gear shifting oil cylinder 2 performs the following four course of work:
Process is 1. --- middle position to right position, i.e., hang from neutral gear N to the process of R/1/3/5/7 shelves, that is, hang shelves process;
Process is 2. --- right position to middle position, i.e., pluck from R/1/3/5/7 shelves to the process of neutral gear N, that is, pluck a grade process;
Process is 3. --- middle position to left position, i.e., hang from neutral gear N to the process of C/2/4/6/8 shelves, that is, hang shelves process;
Process is 4. --- left position to middle position, i.e., pluck from C/2/4/6/8 shelves to the process of neutral gear N, that is, pluck a grade process.
More than, Zuo Wei, right position and middle position each mean the movement position of piston rod, respectively limit on the left position, limit on the right-right-hand limit position Put and centre position.
According to the operation principle of the operation principle and synchronized of above gear shifting oil cylinder 2, magnetic valve HSV during each3、 HSV4Running order it is as shown in table 2:
2 each process magnetic valve action logic of table
In the design process of gear shifting oil cylinder 2, it is most important that the selection of dimensional parameters, the i.e. output end of piston rod 21 are straight Footpath d1, gear shifting oil cylinder B chambers internal diameter d2, piston 22 internal diameter d3, gear shifting oil cylinder A chambers internal diameter(Namely the external diameter of piston 22)d4 With the casing wall thickness h in gear shifting oil cylinder A chambers.Gear shifting oil cylinder 2 is made on the basis of active force, actuation time and intensity is met, volume Reduce as far as possible, to meet requirement of the AMT hydraulic shifters at aspects such as berth-changing strength, shift time and reliabilities.Table 3 below is carried Other known parameters of gear shifting oil cylinder 2 are supplied.
3 oil cylinder of table designs known parameters
How below will be explained in detail by setting up CO models, determine the size of AMT hydraulic shifters.
1st, the CO models of AMT hydraulic shifters are set up
Used as multilevel optimization's method of coupled system, CO models have system-level and subsystem irrespective of size two-stage optimizing structure.Top With system goal function as optimization aim, constraints is consistency constraint between each subsystem to the system-level optimizer of layer, so as to Coordinate the optimum results of each subsystem;Subsystem irrespective of size optimizer is using system level design variable desired value and the subsystem optimization solution Difference as optimization object function, constraints is the constraint related to this subsystem.
Hereinafter still by taking gear shifting oil cylinder 2 as an example will illustrate how to set up CO models, and realize setting for AMT hydraulic shifters Meter.In view of bit selecting oil cylinder 1 is identical with the version of gear shifting oil cylinder 2, simply dimensional parameters are different, and here is no longer gone to live in the household of one's in-laws on getting married State.
The 1.1 CO models for setting up gear shifting oil cylinder 2
Illustrate by taking gear shifting oil cylinder 2 as an example, application of the Analysis for CO model in the design of AMT hydraulic shifters, Fig. 5 Show the CO models of gear shifting oil cylinder 2.
With the volume of gear shifting oil cylinder 2 as optimization design target;Design requirement meets power, time, working strength etc. for oil cylinder Constraints;Design variable is the internal diameter and wall thickness of hydraulic cylinder, is set to vector x={ d1,d2,d3,d4,h};The working face of each oil pocket Product is as follows.
Represent the internal diameter d of piston 223Corresponding area, when piston rod 21, by middle position, displacement is moved to the right (Or moved from right position to middle position)When, active area of the A chambers inner fluid to piston rod 21;
Represent that displacement is moved to the right by middle position when piston rod 21(Or moved from right position to middle position)When, B Active area of the chamber inner fluid to piston rod 21;
Represent the outside diameter d of piston 224Corresponding area, when piston rod 21 is moved from middle position to left dislocation(Or Moved from left position to middle position)When, active area of the A chambers inner fluid to piston rod 21.
Thus the optimization CO models of gear shifting oil cylinder 2 are set up, as shown in Figure 5:System layer is economy model, with gear shifting oil cylinder 2 volume is used as optimization aim;Subsystem layer is respectively mechanical model, kinetic model and reliability model, represents respectively and carries The constraints of lotus, time and working strength.
The object function of system, i.e. volume F (z) of the simplified model of gear shifting oil cylinder 2 is:
Constraints(That is system-level compatibility constraint)JiFor:
Here, length of the l for hydraulic shift oil cylinder 2, by gear shift stroke lx and magnetic valve(HSV3And HSV4)Spacing determine It is fixed, i.e. l=lx+l1+2l0.Constraints Ji is also i-th(Wherein i=1,2,3)The object function of individual subsystem;zj, xij *Respectively It is system-level and subsystem irrespective of size design variable vector.
The object function of subsystem is:
The constraints that subsystem need to meet is:
ci(xi)≤0 (4)
Here, xiFor subsystem design variable:x1={d1,d2,d3,d4},x2={d1,d2,d3,d4},x3={d1,d2,d4, h }, zj *For element in the optimum results of system layer, xijFor j-th design variable of i-th subsystem, c1, c2, c3Correspond to respectively and carry Lotus, time, the relevant constraint under intensity requirement.First, it is system-level to subsystem level distribution design vector desired value Z, son System i is meeting its own constraints ci(xiOn the premise of)≤0, ask for its design variable and the subsystem is supplied to system-level Difference minimum of a value between the desired value of system, and by optimum results XiReturn to system-level.It is system-level to be returned according to subsystem irrespective of size Design vector XiUniformity equality constraint J between construction subsystemiZ (), under its constraints, asks for system goal function F The minimum of a value of (z), and optimum results Z ' is again passed to into subsystem irrespective of size.Between system-level optimization and the optimization of subsystem irrespective of size Successive ignition, finally gives an optimum system design scheme.
More than, X is the optimum results after each subsystem often walks iterative calculation.Subsystem design variable x={ d1,d2,d3,d4, H } through the calculated optimum results of optimization of subsystem, i.e. subsystem unification group single step optimal value { d1,d2,d3,d4, h } it is designated as X。
More than, Z is the optimum results after system layer often walks iterative calculation.System level design variable z={ d1,d2,d3,d4,h} Through the calculated optimum results of the optimization of system layer, i.e. one group of single step optimal value { d of system layer1,d2,d3,d4, h } and it is designated as Z.
In this specific embodiment, according to the CO models of above-mentioned optimization, how illustrate system layer with subsystem layer is Determine the dimensional parameters vector x={ d of shift cylinder 21,d2,d3,d4, h }.
1.2 system layer(sys)Optimization CO models
System layer optimization CO models are economy model, the volume with shift cylinder as design object, its mathematical optimization mould Type includes two parts:The system goal function and subsystem consistency constraint of optimization, as shown in following formula:
Here, F (z) is the system goal function for needing optimization;Length of the l for hydraulic shift oil cylinder 2, by gear shift stroke lx And magnetic valve(HSV3And HSV4)Spacing determine;JiIt is consistency constraint, and the object function of i-th subsystem.diTo be The design variable of system layer, d1i *For the optimum results X of the first subsystem irrespective of size1Middle element, d2i *Optimization for the second subsystem irrespective of size is tied Fruit X2Middle element, d31 *、d32 *、d34 *、h3 *For the optimum results X of the 3rd subsystem irrespective of size3Middle element.
The optimization of system layer is substantially to find new vector Z so as to more previous vector Z ' closer to the optimal solution of original problem, This causes each subsystem to optimize the desired design vector X of the subsystem for obtaining according to vector Z1, X2, X3Between inconsistent degree by Gradually reduce, thus the uniformity equality constraint adopted in system-level optimization problem, i.e. Ji(z)=0.This is kind of a perfect condition, only Have and just meet when vector Z is close to the optimal solution of original problem.And in general, be to be unsatisfactory for Ku En-Plutarch(Kuhn- Tucker)Condition, system-level equality constraint Lagrange(Lagrange)Multiplier is not present, and is without solution.
It is this according to the inconsistent information between subsystem, constructing system level dynamic slave algorithm is as follows:
It is the inconsistent information between subsystem to define Δ:
Δ=| | X1-X2||+||X2-X3||+||X3-X1|| (6)
Make slack:δ=(λ × Δ)2, wherein 0.5 < λ < 1(7)
Then original system layer constraints is converted into:
Former uniformity equality constraint is changed into inequality constraints, and δ is a dynamic amount, can be with the inconsistent information between subsystem Δ is continually changing, and diminishes with Δ, and δ reduces, and the next step optimizing for design vector provides suitable scope, makes X1、X2、X3By Step tends to consistent.
1.3 subsystems 1(sub1)Optimized model
The optimization CO models of subsystem 1 should meet mechanical requirements, gear shift oil for mechanical model, the i.e. design of gear shifting oil cylinder 2 Cylinder 2 acts on the power on piston rod 21 and should be able to overcome the berth-changing strength corresponding to each gearshift procedure.Process 1 and process 3 are extension Shelves process, the output action power of gear shifting oil cylinder 2 should be able to overcome its maximum gear engaging power, process 2 and process 4 to pluck a grade process, the mistake Journey resistance is little, takes the 20% of maximum berth-changing strength.Maximum berth-changing strength is by the gain of parameter in former manual mode, the extension shelves of gear shifting handle Active force is 250N to the maximum, and Jing original armstrong's patent structures are transformed into the active force of the application point of the piston rod 21 of shift cylinder 2 and are 1700N, i.e., the required maximum berth-changing strength for overcoming.According to table 2 it is each during magnetic valve action logic table, grade process point will be plucked For 2 stages:Front 70% need to overcome and pluck a grade power, as long as 30% can guarantee that piston 22 is moved toward middle position afterwards, here selection overcomes Resistance is 50N.According to the mechanical relationship of each process, Mathematical Modeling as follows is set up:
Wherein, FmFor each the output of process active force of oil cylinder, m=1,2,3,4, FmSubscript 1,2 represent former and later two mistakes respectively Journey;SnFor the effective work area of corresponding process, n=1,2,3;P is oil sources principal pressure, is determined by system oil sources, is not belonging to AMT liquid The pressure controllable parameter of shifter itself, not in optimization range, output oil pressure is changing value P ∈ [4, a 4.5] Mpa, this tool Oil pressure minimum of a value is selected to calculate in body embodiment;P00 is taken as fuel tank oil pressure;FmaxFor maximum berth-changing strength 1700N.
1.4 subsystems 2(sub2)Optimized model
The optimization CO models of subsystem 2 are dynamic property model.Dynamic property is mainly embodied by shift time, time mistake Long, power interruption is long, and power performance declines;Time is too short, easily produces shifting shock, affects gear shift ride comfort, therefore will Ask shift time meet suitable span, according to a large amount of train experiments, shift time t should be controlled within 0.3s.
Gearshift procedure is kinematic nonlinearity process, and oil pressure, flow etc. are all time-varying parameters, it is impossible to when accurately asking its gear shift Between, this specific embodiment is reduced at the uniform velocity process and is carried out approximate calculation.Process 1 and process 3 only need control to hang shelves process Unilateral oil pocket is oil-filled, and front 80% stroke, to eliminate idle stroke, load is less to take 340N;Process 2 and process 4 are to pluck neutral gear Process, is to realize quickly plucking shelves, and front 70% stroke one side oil pocket is oil-filled, and 30% stroke both sides oil pocket is simultaneously oil-filled afterwards.With process 2 As a example by carry out shift time solve explanation, obtained by equilibrium equation:
Due to piston movement speed it is equal, i.e.,:Qa/S1=Qb/S2(11)
Meanwhile, can be obtained according to flow and pressure reduction relation:
BeforeAfterwards
Simultaneous formula(7)、(8)、(9)The oil pressure in A chambers during cylinder efficient can be tried to achieve:
Wherein, τ=S1/S2,F1=340N.
Simultaneous formula(12)With(13)The actuation time of process 2 can be obtained:
In the same manner, oil pressure in the chamber of other three processes can be tried to achieve, setup time is the Mathematical Modeling of constraint, as follows:
Wherein, Pɑ、PbThe oil pressure in hydraulic shift cylinder A, B chambers is represented respectively, and subscript 1,2 represents former and later two work respectively Stage;tjRepresent the shift time of four gear shift strokes.
1.5 subsystems 3(sub3)Optimized model
The optimization CO models of subsystem 3 are reliability model.Can be obtained by mechanical design handbook, its reliability is mainly reflected in The strength check with piston rod 21 is checked in the check of intensity, i.e. wall thickness, when piston rod 21 adopts thread connection, the danger of piston rod 21 Dangerous section is at Gewindefreistiche.According to mechanical design handbook, can obtain its mathematic optimal model is:
Wherein, δ is casing wall thickness allowable;F represents the maximum tension stress of piston rod 21, the piston rod 21 of corresponding process 3 Active force;d0For the end thread internal diameter d of piston rod 210=d1- 1.0825e, e are pitch;σnRepresent that the danger of piston rod 21 cuts At face(At Gewindefreistiche)Combined stress;[σ] is allowable stress, [σ]=σs/n2, σsFor screw thread yield point, n2For safety system Number.
CO models can be set up using two kinds of components of Optimization and Matlab.Calculating process need to be in system layer Initializaing variable value assignment is given in Optimization components.Can be according to load F1Select d3Size, further according between each size Magnitude relationship(h<d1<d3<d2<d4), select one group of initial value.
In this specific embodiment, select each variable initial value to be followed successively by 10,20,35,40,50mm.System layer and subsystem The model optimization algorithm of layer selects Genetic Algorithms, calculates through 1494 times, obtains result shown in table 4.As hydraulic cylinder is Standard component, its dimensional parameters have the span of standard.Therefore optimal design parameter is obtained using following methods:Set according to machinery Two groups of close variable-values of meter handbook selection and optimization result, by the checking of subsystem layer Mathematical Modeling, selection meets bar The relatively figure of merit of part, the design result after being optimized(It is shown in Table 4).
The optimum results of 4 design variable of table
The design of bit selecting oil cylinder is equally also required to consider the constraintss such as bit selecting time, bit selecting power, reliability, therefore also adopts With the method for designing similar with shift cylinder.Due to the design parameter and method of bit selecting oil cylinder it is similar with gear shifting oil cylinder, no longer Repeat specification.
Can be seen that from data before and after the optimization of upper table 4:The result obtained by the method for the present invention and structure phase before Than cylinder sizes are obviously reduced, and so as to reduce the volume of AMT hydraulic gear-shiftings mechanism, reduce cost.Due to cylinder cavity chi Very little corresponding reduction, then the hydraulic oil volume that single is used during hanging shelves is also reduced, and then fluid loss is reduced, improve oil The operating efficiency of cylinder.
As can be seen from Table 5, the oil cylinder output action power before and after optimization can meet berth-changing strength requirement, power after optimization It is relatively small, improve the effective rate of utilization of oil cylinder;After optimization, each process action time relatively optimizes front overall reduction and can guarantee that In 250ms, shorten shift time, reduce the time of power interruption, improve the dynamic property of vehicle.
The contrast of oil cylinder berth-changing strength and actuation time before and after the optimization of table 5
Therefore, the method for designing of the present invention is forward design method, according to cooperative optimization method, determines target letter Number, progressively converges to optimal solution by alternative manner under the conditions of meet the constraint.Compared with proof method is gathered in the examination of traditional design, mesh Indicate.
The above, the only specific embodiment of the present invention, but protection scope of the present invention is not limited thereto, any Those familiar with the art the invention discloses technical scope in, change or replacement can be readily occurred in, should all be contained Cover within protection scope of the present invention.Therefore, protection scope of the present invention described should be defined by scope of the claims.

Claims (4)

1. a kind of method for designing of automatic mechanical transmission AMT hydraulic shifters, the AMT hydraulic shifters include oil Cylinder, it is characterised in that methods described includes:
Collaboration optimization CO models are built for the oil cylinder in the AMT hydraulic shifters, the CO models include system-level target Function and three subsystems level object function;
By iterative calculation, the optimal solution of the CO models is determined, wherein optimal solution determination for needed for the oil cylinder Dimensional parameters vector;
According to the dimensional parameters vector of the oil cylinder, the size of the AMT hydraulic shifters is determined;
Wherein, the oil cylinder in the AMT hydraulic shifters builds CO models, including:
Build the system goal function of the oil cylinder
Build the subsystem objectives function of the oil cylinder
Here, l is the length of the oil cylinder, xiFor subsystem design variable:x1={ d1,d2,d3,d4},x2={ d1,d2,d3, d4},x3={ d1,d2,d4, h }, zj *For element in the optimum results of system layer, xijJ-th design for i-th subsystem becomes Amount, d1For the output end diameter of piston rod, d2For the internal diameter in the B chambers of oil cylinder, d3For the internal diameter of piston, d4For in the A chambers of oil cylinder The external diameter of footpath or piston, the casing wall thickness in the A chambers that h is oil cylinder;
Wherein, by iterative calculation, determine the optimal solution of the CO models, including:
It is system-level to three subsystems level distribution design vector desired value Z, the subsystems in the three subsystems level exist On the premise of meeting its own constraints, ask for respectively its design variable and the system-level desired value for being supplied to the subsystem it Between difference minimum of a value, and by optimum results XiReturn to system-level, wherein i=1,2,3;
The system-level optimum results X returned according to the three subsystems leveliConsistency constraint between construction subsystem, in its constraint Under the conditions of, ask for the minimum of a value of system goal function, and optimum results Z ' is again passed to subsystem irrespective of size as new design to Amount desired value;
Successive ignition between system-level optimization and the optimization of subsystem irrespective of size, finally determines the optimal solution of the CO models.
2. method according to claim 1, it is characterised in that the optimal solution of the determination CO models, including:
According to consistency constraint condition, the optimal solution of the system goal function of the oil cylinder is determined;
According to load restraint condition, time constraint condition and strength constraint condition, the subsystem objectives function of the oil cylinder is determined Optimal solution.
3. method according to claim 2, it is characterised in that described according to consistency constraint condition, determines the oil cylinder System goal function optimal solution, including:
min F ( z ) = &pi; ( d 4 2 + h ) 2 ( l + 0.006 )
s . t . J 1 = &Sigma; i = 1 4 ( d i - d 1 i * ) 2 &le; &delta; J 2 = &Sigma; i = 1 4 ( d i - d 2 i * ) 2 &le; &delta; J 3 = ( d 1 - d 31 * ) 2 + ( d 2 - d 32 * ) 2 + ( d 4 - d 34 * ) 2 + ( h - h 3 * ) 2 &le; &delta;
Wherein, F (z) is the system goal function for needing optimization;diFor the design variable of system layer:d1For the output end of piston rod Diameter, d2For the internal diameter in the B chambers of oil cylinder, d3For the internal diameter of piston, d4It is oil for the external diameter of the internal diameter or piston in the A chambers of oil cylinder, h The casing wall thickness in the A chambers of cylinder, l is the length of the oil cylinder, J1It is the object function of the first subsystem irrespective of size, J2It is the second subsystem The object function of level, J3It is the object function of the 3rd subsystem irrespective of size, d1i *For the optimum results X of the first subsystem irrespective of size1Middle element, d2i *For the optimum results X of the second subsystem irrespective of size2Middle element, d31 *、d32 *、d34 *、h3 *For the optimum results X of the 3rd subsystem irrespective of size3 Middle element, δ are the dynamic amounts that a meeting is continually changing with the inconsistent information between subsystem.
4. method according to claim 2, it is characterised in that it is described according to load restraint condition, time constraint condition and Strength constraint condition, determines the optimal solution of the subsystem objectives function of the oil cylinder, including:
According to load restraint condition, the optimal solution of the first subsystem objectives function of the oil cylinder is determined;
According to time constraint condition, the optimal solution of the second subsystem objectives function of the oil cylinder is determined;
According to strength constraint condition, the optimal solution of the 3rd subsystem objectives function of the oil cylinder is determined.
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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7437225B1 (en) * 2005-07-29 2008-10-14 Rockwell Collins, Inc. Flight management system
CN101714182A (en) * 2008-12-29 2010-05-26 北京航空航天大学 Integration method of collaborating assembly design, process planning and simulation verification of complicated product
CN102024082A (en) * 2010-12-15 2011-04-20 同济大学 Method for realizing multidisciplinary and multi-objective optimization of structural system of automobile instrument panel
CN103455692A (en) * 2013-09-29 2013-12-18 吉林大学 Two-step optimization design method for automotive body section shape
GB2505416A (en) * 2012-08-28 2014-03-05 Jaguar Land Rover Ltd Computer implemented method of engine design optimisation

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7437225B1 (en) * 2005-07-29 2008-10-14 Rockwell Collins, Inc. Flight management system
CN101714182A (en) * 2008-12-29 2010-05-26 北京航空航天大学 Integration method of collaborating assembly design, process planning and simulation verification of complicated product
CN102024082A (en) * 2010-12-15 2011-04-20 同济大学 Method for realizing multidisciplinary and multi-objective optimization of structural system of automobile instrument panel
GB2505416A (en) * 2012-08-28 2014-03-05 Jaguar Land Rover Ltd Computer implemented method of engine design optimisation
CN103455692A (en) * 2013-09-29 2013-12-18 吉林大学 Two-step optimization design method for automotive body section shape

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
协同优化理论及其在铰接式自卸车驱动桥设计中的应用;仝令胜;《中国博士学位论文全文数据库 工程科技Ⅱ辑》;20091015(第10期);第C035-3页 *

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