CN113111449A - Mechanical transmission static gear shifting simulation method based on AMESim - Google Patents
Mechanical transmission static gear shifting simulation method based on AMESim Download PDFInfo
- Publication number
- CN113111449A CN113111449A CN202110257756.4A CN202110257756A CN113111449A CN 113111449 A CN113111449 A CN 113111449A CN 202110257756 A CN202110257756 A CN 202110257756A CN 113111449 A CN113111449 A CN 113111449A
- Authority
- CN
- China
- Prior art keywords
- shifting
- gear
- force
- gear shifting
- groove
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000000034 method Methods 0.000 title claims abstract description 56
- 238000004088 simulation Methods 0.000 title claims abstract description 52
- 230000009347 mechanical transmission Effects 0.000 title claims abstract description 33
- 230000003068 static effect Effects 0.000 title claims abstract description 33
- 238000011156 evaluation Methods 0.000 claims abstract description 35
- 238000000418 atomic force spectrum Methods 0.000 claims abstract description 25
- 238000013461 design Methods 0.000 claims abstract description 24
- 230000008569 process Effects 0.000 claims abstract description 17
- 238000005094 computer simulation Methods 0.000 claims abstract description 9
- 238000006073 displacement reaction Methods 0.000 claims description 27
- 230000007246 mechanism Effects 0.000 claims description 23
- 238000012360 testing method Methods 0.000 claims description 15
- 229910000831 Steel Inorganic materials 0.000 claims description 11
- 239000010959 steel Substances 0.000 claims description 11
- 230000008859 change Effects 0.000 claims description 8
- 230000007935 neutral effect Effects 0.000 claims description 6
- 238000009434 installation Methods 0.000 claims description 4
- 238000013016 damping Methods 0.000 claims description 3
- 230000007704 transition Effects 0.000 claims description 3
- 101100001669 Emericella variicolor andD gene Proteins 0.000 claims description 2
- 230000006835 compression Effects 0.000 claims description 2
- 238000007906 compression Methods 0.000 claims description 2
- 230000005540 biological transmission Effects 0.000 abstract description 9
- 238000012938 design process Methods 0.000 abstract description 4
- 238000010586 diagram Methods 0.000 description 8
- 238000005457 optimization Methods 0.000 description 7
- 238000002474 experimental method Methods 0.000 description 5
- 230000009471 action Effects 0.000 description 4
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000284 extract Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000009191 jumping Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
Images
Classifications
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/17—Mechanical parametric or variational design
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/02—Reliability analysis or reliability optimisation; Failure analysis, e.g. worst case scenario performance, failure mode and effects analysis [FMEA]
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/20—Design reuse, reusability analysis or reusability optimisation
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Theoretical Computer Science (AREA)
- General Physics & Mathematics (AREA)
- Evolutionary Computation (AREA)
- Computer Hardware Design (AREA)
- General Engineering & Computer Science (AREA)
- Pure & Applied Mathematics (AREA)
- Mathematical Optimization (AREA)
- Mathematical Analysis (AREA)
- Computational Mathematics (AREA)
- Gear-Shifting Mechanisms (AREA)
Abstract
The invention relates to a gear shifting simulation method of a transmission, in particular to an AMESim-based mechanical transmission static gear shifting simulation method, which solves the technical problems that in the design process of the existing mechanical transmission, the gear shifting force of all positions in the whole gear shifting process cannot be accurately predicted, the whole gear shifting force curve cannot be accurately calculated, the design period of gear shifting related parts of the transmission is long, and the cost is increased. The method comprises the following steps: establishing a dynamic simulation model of the static gear shifting process of the mechanical transmission based on AMESim; acquiring initial design parameters of three grooves of the mechanical transmission and objective evaluation indexes of a gear shifting force curve; inputting the initial design parameters into a dynamic simulation model for simulation; and continuously performing iterative simulation according to the objective evaluation index of the gear shifting force curve to obtain the optimized matching scheme of the groove size and the spring parameter.
Description
Technical Field
The invention relates to a gear shifting simulation method of a transmission, in particular to a static gear shifting simulation method of a mechanical transmission based on AMESim.
Background
And self-locking devices are uniformly arranged in the mechanical transmission and are used for preventing automatic gear jumping and gear disengaging. The self-locking device is composed of a self-locking steel ball and a self-locking spring, three grooves are generally designed on the surface of a shifting fork shaft or a shifting block, when the shifting fork shaft or the shifting block moves to a neutral gear or a certain working position, one groove is required to be just aligned to the self-locking steel ball, and the steel ball is embedded into the groove under the action of the spring pressure, so that the shifting fork shaft or the shifting block cannot be separated out automatically and is kept at a certain shifting position. In the process of shifting gears, the design of groove shape and the matching of spring have great influence to the power of shifting gears, and unreasonable matching can lead to the power of shifting gears too big or undersize, shift the jamming, shift and have a pause and frustrate sense, influence the driver and shift and feel.
At present, subjective evaluation is mainly used for evaluating the gear shifting performance, corresponding objective indexes comprise gear shifting force peak value force and stroke, gear engaging rigidity, gear suction rigidity, gear disengaging return rigidity and the like, all the indexes can be embodied in a gear shifting force curve, and the static gear shifting force curve of the transmission can be accurately predicted and is of great importance for evaluating the static gear shifting performance. In the actual design process, the shape of the groove is generally designed through experience, the spring is matched, the shifting force of the point is calculated according to the fact that the gear is shifted to a certain fixed position, the shifting force of all positions in the whole gear shifting process cannot be accurately predicted, and the whole shifting force curve cannot be accurately calculated. The optimization and improvement are mostly carried out according to experimental test results or subjective evaluation of drivers, so that the problems of long optimization design period, cost increase and the like are brought.
Chinese patent CN110309614A discloses a shift simulation method for a synchronizer, which mainly focuses on dynamic shift performance, including a dynamic model of a synchronizer coupling process, and does not give detailed modeling for a self-locking structure and a synchronizer compression spring structure related to a static shift force. In addition, the driving system robot model of the simulation model only carries out feedback control through speed, and the actual gear shifting force curve cannot be accurately calculated.
Disclosure of Invention
The invention aims to solve the technical problems that the gear shifting force of all positions in the whole gear shifting process cannot be accurately predicted and the whole gear shifting force curve cannot be accurately calculated in the design process of the conventional mechanical transmission, so that the design period of parts related to gear shifting of the transmission is long and the cost is increased.
The technical idea of the invention is as follows: according to the method for carrying out simulation modeling on the gear shifting structure, a gear shifting force curve is calculated according to the initial groove shape and the spring parameters, and the groove size and the spring parameters are optimized according to the size of objective evaluation indexes.
In order to achieve the purpose, the invention adopts the technical scheme that:
a static gear shifting simulation method of a mechanical transmission based on AMESim is characterized by comprising the following steps:
the initial design parameter is the size of the groove, and the size of the groove is stored as an XYR data format file;
the objective evaluation indexes of the gear shifting force curve comprise maximum gear shifting force, maximum gear picking force, gear engaging suction rigidity, gear picking suction rigidity and gear engaging force requirements; the gear engaging force is required to be gradually increased and only one peak point exists in the process from neutral gear engagement to maximum acting force;
and 4, continuously performing iterative simulation according to the objective evaluation index of the gear shifting force curve to obtain the optimized matching scheme of the groove size and the spring parameter.
Further, in step 1, the shifting force model of the test bed shifting force, displacement and speed closed-loop feedback control actuating mechanism equivalent model 13 is:
wherein: f is the shifting force of the actuating mechanism, K is the equivalent stiffness of the actuating mechanism, c is the equivalent damping coefficient of the actuating mechanism, x is the shifting displacement,
is the shift speed.
Further, in step 4, continuously performing iterative simulation according to the objective evaluation index of the gear shifting force curve, specifically performing the iterative simulation according to the following method:
1) objective evaluation index: maximum shift force;
the method comprises the following steps: when the maximum shifting force is increased, at least one parameter selected from D8 ≠ D10 ℃ and D12 ℃,; at least one parameter change of the alternative D1 ↓, D2 ↓, D3 ↓, D4 ↓, D6 ↓, and D7 ↓;
2) objective evaluation index: gear engaging suction stiffness;
the method comprises the following steps: increasing the geared suction stiffness, preferably D9 ↓and/or D11 ↓; at least one parameter change of alternative D1 ↓, D5 ↓, and D6 ↓;
3) objective evaluation index: maximum gear-disengaging force;
the method comprises the following steps: when the maximum gear engaging force is reduced, at least one parameter of D8 ≠ D10 ℃ D12 ℃;
4) objective evaluation index: the suction rigidity is picked up;
the method comprises the following steps: when the gear-shifting suction rigidity is increased, the preferred D13 ↓and/or D11 ↓; at least one parameter change of alternative D1 ↓, D5 ↓, and D6 ↓;
5) objective evaluation index: in the process from neutral gear starting to gear engagement to maximum acting force, gear engagement force is gradually increased, and only one peak point exists;
the method comprises the following steps: d9 ↓, D11 ↓, D3 ↓, D4 ↓, D5 ↓andD 6 ↓;
wherein: defining the position where the central axis of the cross section of the shifting block passes through as a coordinate origin, and D1 is the chamfer radius of the highest point of the groove of the shifting block; d2 is the x-direction size of the highest point of the shifting block groove; d3 is the y-direction size of the highest point of the shifting block groove; d4 is the y-direction size of the intersection point of the central lines of the two inclined planes of the shifting block groove; d5 is the horizontal included angle of the inclined plane of the groove of the shifting fork shaft; d6 is the chamfer radius of the highest point of the groove of the shifting fork shaft; d7 is the vertical included angle of the slide sleeve groove inclined plane; d8 is the mounting pressure of the shifting block self-locking spring; d9 is the rigidity of the shifting block self-locking spring; d10 is the mounting pressure of the self-locking spring of the shifting fork shaft; d11 is the self-locking spring stiffness of the shifting fork shaft; d12 is spring installation pressure of a synchronizer pressure spring structure; d13 is spring stiffness of a synchronizer pressure spring structure; ×) indicates a parameter increase; ↓ represents parameter reduction;
and the iterative simulation of the objective evaluation indexes of the gear shifting force curve has no sequence.
Further, in step 2, the size of the groove is formed by connecting equivalent section outlines of the groove into a plurality of line segments, and a group of sizes of chamfer arc transition is arranged at the position of an inflection point.
Further, in step 4, the spring parameters include initial installation pressure and stiffness of each spring.
Further, in step 1, the simulation model is built by a mechanical library module in AMESim.
The invention has the beneficial effects that:
1) according to the static gear shifting simulation method of the mechanical transmission based on the AMESim, the main factors influencing the gear shifting performance are analyzed through a method combining experiments and simulation, an accurate simulation model is established based on AMESim software, the gear shifting force curve can be predicted at the beginning of design, the repeated trial-manufacture, experiment and improved cyclic design process can be effectively reduced, the experiment cost is reduced to the greatest extent, and manpower and material resources are saved.
2) The simulation method provided by the invention is adopted to effectively simulate the variables such as the shifting force, the shifting displacement, the shifting speed and the like in the shifting process, the errors of the maximum shifting force and the maximum gear-disengaging force and the experimental result under the working condition of each gear are smaller, the maximum error is within 10%, and the consistency of the shifting force curve and the experimental result is better.
3) By the AMESim-based mechanical transmission static gear shifting simulation method, the structure of the part, the parameters of a spring and the like of the existing product are optimized, designed and improved, the problem of poor operating hand feeling of the transmission is effectively solved, the product quality is improved, and the after-sale failure rate is reduced.
Drawings
FIG. 1 is a flow chart of a mechanical transmission static shift simulation method based on AMESim according to the invention;
FIG. 2 is a schematic illustration of a mechanical transmission static shifting configuration of the present invention;
FIG. 3 is a schematic diagram of an AMESim-based mechanical transmission static shift dynamics simulation model in the invention;
FIG. 4 is a schematic diagram of a test stand shift force, displacement and speed closed loop feedback control actuator according to the present invention;
FIG. 5 is a schematic diagram of the shifting force and shifting displacement during a static shifting of the mechanical transmission according to an embodiment of the present invention;
FIG. 6 is a schematic diagram showing comparison between simulation results and test results before and after optimization of a "shifting force-displacement curve" in the embodiment of the present invention;
FIG. 7 is a graphical representation of the results of FIG. 6 before optimization of the "shift force-displacement curve";
FIG. 8 is a graphical representation of the optimized shift force-displacement curve of FIG. 6;
FIG. 9 is a graphical representation of the results of the "shift force-displacement curve" experiment of FIG. 6;
FIG. 10 is a schematic diagram illustrating the dimensions of a recess structure of the pick in an embodiment of the present invention; d1, D2, D3 and D4 are designed sizes which have relatively large influence on gear shifting force;
FIG. 11 is a schematic diagram illustrating the dimensions of a fork shaft groove structure according to an embodiment of the present invention; wherein D5 and D6 are designed sizes which have relatively large influence on gear shifting force;
FIG. 12 is a schematic view showing the structural dimensions of a groove of the sliding sleeve according to an embodiment of the present invention; among them, D7 is a design size that has a relatively large influence on the shifting force.
Description of reference numerals:
1-a shifting block self-locking structure, 2-a first steel ball, 3-a shifting block, 4-a shifting fork shaft, 5-a guide block, 6-a shifting fork, 7-a sliding sleeve, 8-a swing pin, 9-a transverse gear shifting rod, 10-a shifting fork shaft self-locking structure, 11-a second steel ball and 12-a synchronizer pressure spring structure;
13-a test bed shifting force, displacement and speed closed loop feedback control actuating mechanism equivalent model, 14-a shifting block self-locking structure model, 15-a shifting fork shaft self-locking structure model and 16-a synchronizer pressure spring structure model;
d1-highest chamfer radius of the groove of the shifting block, D2-highest x-direction dimension of the groove of the shifting block, D3-highest y-direction dimension of the groove of the shifting block, D4-y-direction dimension of intersection point of center lines of two inclined planes of the groove of the shifting block, D5-horizontal included angle of inclined plane of the groove of the shifting fork shaft, D6-highest chamfer radius of the groove of the shifting fork shaft and D7-vertical included angle of inclined plane of the groove of the sliding sleeve.
Detailed Description
In order to more clearly explain the technical solution of the present invention, the following detailed description of the present invention is made with reference to the accompanying drawings and specific examples.
According to the actual structure, the invention forms a simulation modeling method, can predict the gear shifting force curve, extracts objective evaluation indexes corresponding to subjective evaluation indexes from the gear shifting force curve, reduces the design-experiment-improved cycle process and improves the static gear shifting performance.
As shown in FIG. 1, the invention discloses a static gear shifting simulation method of a mechanical transmission based on AMESim, which comprises the following steps:
step 1: and establishing a dynamic model of the static gear shifting process, which comprises a test bed gear shifting force, displacement and speed closed loop feedback control actuating mechanism equivalent model 13, a shifting block self-locking structure model 14, a shifting fork shaft self-locking structure model 15 and a synchronizer pressure spring structure model 16.
As shown in fig. 2, the static gear shifting mechanism of the mechanical transmission mainly comprises a shifting block self-locking structure 1, a shifting fork shaft self-locking structure 10 and a synchronizer pressure spring structure 12. When shifting gears, the outer rocker arm drives the transverse shift lever 9 and the shifting block 3 to rotate, meanwhile, the shifting fork shaft 4 is pushed to move axially through the guide block 5, the shifting fork 6 fixedly connected with the shifting fork shaft 4 drives the sliding sleeve 7 to move axially, and the shifting fork is moved to a certain fixed position from left to right to realize gear shifting.
Wherein, the shifting block self-locking structure 1 consists of a shifting block groove, a first steel ball 2 and a spring. When the shifting block 3 rotates, the first steel ball 2 moves along the surface of the groove, and resistance is generated under the action of spring pressure.
The fork shaft self-locking structure 10 consists of a fork shaft groove, a second steel ball 11 and a spring. When the shifting fork shaft 4 moves axially, the second steel ball 11 moves along the surface of the groove, and resistance is generated under the action of spring pressure.
Meanwhile, the synchronizer pressure spring structure 12 consists of a groove on the sliding sleeve 7, a swing pin 8 and a spring. When the sliding sleeve 7 moves axially, the swing pin 8 moves along the surface of the groove, and resistance is generated under the action of spring pressure.
Considering the three-part module in combination, a dynamic simulation model of the static gear shifting mechanism of the mechanical transmission based on AMESim is established and is shown in FIG. 3. Physical models such as a test bed shifting force, displacement and speed closed-loop feedback control actuating mechanism equivalent model 13, a shifting block self-locking structure model 14, a shifting fork shaft self-locking structure model 15 and a synchronizer pressure spring structure model 16 are built by a mechanical library module in AMESim, and the synchronizer pressure spring structure model 16 comprises three groups of analog synchronizer pressure spring structures.
The shifting force model of the equivalent model 13 of the test bed shifting force, displacement and speed closed-loop feedback control executing mechanism is shown in the formula (1):
wherein F is the gear shifting force of the actuating mechanism, K is the equivalent rigidity of the gear shifting actuating mechanism, c is the equivalent damping coefficient of the gear shifting actuating mechanism, x is the gear shifting displacement of the actuating mechanism,
is the actuator shift speed.
A schematic diagram of a test bed shifting force, displacement and speed closed-loop feedback control actuator is shown in fig. 4, and in the shifting force model, a maximum shifting speed (Vmax) and a maximum shifting force (Fmax) need to be defined. In FIG. 4, system refers to a bench actuator, which is equivalent to the mass or inertia elements available for actual modeling; the output end out of the transmission is connected with an internal mechanical gear shifting system of the transmission.
Firstly, the ideal gear shifting speed of the actuating mechanism is calculated, see formula (2), and can be obtained by calculating according to the feedback acting force and the set maximum speed:
shift speed obtained by equation (2)
The integral yields the shift displacement x of the actuator.
Then the ideal speed and displacement are feedback controlled, the actual speed and displacement of the actuating mechanism are compared with the ideal gear shifting speed and displacement according to the feedback control principle, and the error is substituted into the formula (1) to calculate the acting force of the actuating mechanism.
Step 2: and acquiring initial design parameters and objective evaluation indexes of a gear shifting force curve.
In the embodiment of the invention, the initial design parameters of three grooves and springs of a certain transmission are obtained and simulated.
Firstly, defining the sizes of three grooves, enabling the shape of the groove to be formed by connecting a plurality of line segments by AMESim software, enabling the position of an intersection point to have chamfer circular arc transition, and storing the size of the shape of the groove into a XYR data format file. As shown in Table 1, the design dimensions are defined in the XYR data format for invocation by the simulation model.
Table 1 groove size definition as XYR format
The sizes of the shifting block, the shifting fork shaft and the sliding sleeve groove are shown in figures 10, 11 and 12, and design sizes D1, D2, D3, D4, D5, D6 and D7 which have relatively large influence on shifting force are marked in the figures. In fig. 10, a position through which a central axis of a cross section of the dial passes is defined as a coordinate origin, wherein D1 is a chamfer radius of a highest point of a groove of the dial; d2 is the x-direction size of the highest point of the shifting block groove; d3 is the y-direction size of the highest point of the shifting block groove; d4 is the y-direction size of the intersection point of the central lines of the two inclined planes of the shifting block groove; in FIG. 11, D5 is the horizontal angle of the inclined plane of the fork shaft groove; d6 is the chamfer radius of the highest point of the groove of the shifting fork shaft; in FIG. 12, D7 is the vertical angle of the groove slope of the sliding sleeve.
The three spring parameters are shown in table 2:
TABLE 2 spring parameters
Objective evaluation indexes of the gear shifting force curve are generally defined according to design requirements, and include the number of peak points, the maximum gear shifting force, the maximum gear disengaging force, the gear engaging suction rigidity, the gear disengaging suction rigidity and the gear engaging force requirements; the gear engaging suction rigidity is the approximate slope of a gear engaging in-place curve from the maximum gear engaging force to the maximum gear engaging force; the gear-off suction rigidity is the approximate slope of a gear-off in-place curve from the maximum gear-off force to the maximum gear-off force; the objective evaluation index in this example has the following requirements:
1) maximum shift force 200 ± 10N;
2) the maximum gear-disengaging force is 160 +/-10N;
3) the gear engaging suction rigidity is 55 +/-10N/mm;
4) the gear-picking suction rigidity is 40 +/-10N/mm;
5) the gear engagement force increases continuously during the process from neutral to maximum gear engagement force, and there is only one peak point in the process.
And step 3: and inputting the initial design parameters into a static gear shifting dynamics simulation module for simulation.
A schematic diagram of the shifting force and shifting displacement during shifting is shown in fig. 4. To ensure the consistency of the simulation and the test, simulation parameters are defined with reference to the experimental conditions, and the relevant parameters are shown in the following table 3:
TABLE 3 simulation parameters
And 4, step 4: and continuously performing iterative simulation according to the objective evaluation index to optimize an ideal parameter matching scheme.
Except for the groove design parameters shown in fig. 10, 11 and 12, the spring parameters also have a large influence on the shifting force curve, all the parameters need to be combined and used in the actual iterative optimization process, the mounting pressure of the shifting block self-locking spring is defined as a parameter D8, the rigidity is defined as D9, the mounting pressure of the shifting fork shaft self-locking spring is defined as a parameter D10, the rigidity is defined as D11, the mounting pressure of the spring of the pressure spring structure of the synchronizer is defined as a parameter D12, and the rigidity is defined as D13. The amount of change in the objective evaluation index due to the influence of the design parameters is shown in Table 4.
TABLE 4 Objective evaluation of index Change for Effect of design parameters
TABLE 5 post optimization groove parameters
TABLE 6 optimized rear spring parameters
The dimensions of the shifting block and the shifting fork shaft and the matching spring are optimized, the optimized groove dimension is shown in table 5, the optimized spring parameter is shown in table 6, and the simulation and test pair of the shifting force-displacement curve is shown in fig. 6.
Table 7 shows objective evaluation indexes of the experimental curves before and after optimization, which are obtained from fig. 7, 8, and 9.
TABLE 7 Objective evaluation index comparison
It can be seen that each optimized evaluation index is close to the design parameter and is well aligned with the test result, and the consistency of the simulation curve and the experiment curve is better.
The above description is only for the purpose of describing the preferred embodiments of the present invention and is not intended to limit the technical solutions of the present invention, and any known modifications made by those skilled in the art based on the main technical concepts of the present invention are within the technical scope of the present invention.
Claims (6)
1. A static gear shifting simulation method of a mechanical transmission based on AMESim is characterized by comprising the following steps:
step 1, establishing an AMESim-based dynamic simulation model of the static gear shifting process of the mechanical transmission; the simulation model comprises a test bed shifting force, displacement and speed closed loop feedback control actuating mechanism equivalent model (13), a shifting block self-locking structure model (14), a shifting fork shaft self-locking structure model (15) and three groups of synchronizer compression spring structure models (16) which are connected in sequence;
step 2, acquiring initial design parameters and objective evaluation indexes of a gear shifting force curve of three grooves of a mechanical transmission shifting block self-locking structure (1), a shifting fork shaft self-locking structure (10) and a synchronizer pressure spring structure (12);
the initial design parameter is the size of the groove, and the size of the groove is stored as a XYR data format file;
the objective evaluation indexes of the gear shifting force curve comprise maximum gear shifting force, maximum gear picking force, gear engaging suction rigidity, gear picking suction rigidity and gear engaging force requirements; the gear engaging force is required to be gradually increased and only one peak point exists in the process from neutral gear engagement to maximum acting force;
step 3, calling initial design parameters to simulate the dynamic simulation model, wherein the simulation parameters comprise maximum gear shifting force, maximum gear shifting displacement, maximum gear shifting speed, equivalent rotational inertia, groove surface elastic modulus and friction coefficient of the steel ball and the groove;
and 4, continuously performing iterative simulation according to the objective evaluation index of the gear shifting force curve to obtain the optimized matching scheme of the groove size and the spring parameter.
2. The AMESim-based mechanical transmission static gear shifting simulation method according to claim 1, wherein the AMESim-based mechanical transmission static gear shifting simulation method comprises the following steps:
in the step 1, a shifting force model of the test bed shifting force, displacement and speed closed loop feedback control actuating mechanism equivalent model (13) is as follows:
wherein: f is the shifting force of the actuating mechanism, K is the equivalent stiffness of the actuating mechanism, c is the equivalent damping coefficient of the actuating mechanism, x is the shifting displacement,
is the shift speed.
3. The AMESim-based mechanical transmission static gear shifting simulation method according to claim 1 or 2, wherein:
in step 4, continuously performing iterative simulation according to the objective evaluation index of the gear shifting force curve, specifically performing the iterative simulation according to the following method:
1) objective evaluation index: maximum shift force;
the method comprises the following steps: when the maximum shifting force is increased, at least one parameter selected from D8 ≠ D10 ℃ and D12 ℃,; at least one parameter change of the alternative D1 ↓, D2 ↓, D3 ↓, D4 ↓, D6 ↓, and D7 ↓;
2) objective evaluation index: gear engaging suction stiffness;
the method comprises the following steps: increasing the geared suction stiffness, preferably D9 ↓and/or D11 ↓; at least one parameter change of alternative D1 ↓, D5 ↓, and D6 ↓;
3) objective evaluation index: maximum gear-disengaging force;
the method comprises the following steps: when the maximum gear engaging force is reduced, at least one parameter of D8 ≠ D10 ℃ D12 ℃;
4) objective evaluation index: the suction rigidity is picked up;
the method comprises the following steps: when the gear-shifting suction rigidity is increased, the preferred D13 ↓and/or D11 ↓; at least one parameter change of alternative D1 ↓, D5 ↓, and D6 ↓;
5) objective evaluation index: in the process from neutral gear starting to gear engagement to maximum acting force, gear engagement force is gradually increased, and only one peak point exists;
the method comprises the following steps: d9 ↓, D11 ↓, D3 ↓, D4 ↓, D5 ↓andD 6 ↓;
wherein: defining the position where the central axis of the cross section of the shifting block passes through as a coordinate origin, and D1 is the chamfer radius of the highest point of the groove of the shifting block; d2 is the x-direction size of the highest point of the shifting block groove; d3 is the y-direction size of the highest point of the shifting block groove; d4 is the y-direction size of the intersection point of the central lines of the two inclined planes of the shifting block groove; d5 is the horizontal included angle of the inclined plane of the groove of the shifting fork shaft; d6 is the chamfer radius of the highest point of the groove of the shifting fork shaft; d7 is the vertical included angle of the slide sleeve groove inclined plane; d8 is the mounting pressure of the shifting block self-locking spring; d9 is the rigidity of the shifting block self-locking spring; d10 is the mounting pressure of the self-locking spring of the shifting fork shaft; d11 is the self-locking spring stiffness of the shifting fork shaft; d12 is spring installation pressure of a synchronizer pressure spring structure; d13 is spring stiffness of a synchronizer pressure spring structure; ×) indicates a parameter increase; ↓ denotes a parameter decrease.
4. The AMESim-based mechanical transmission static gear shifting simulation method according to claim 3, wherein the AMESim-based mechanical transmission static gear shifting simulation method comprises the following steps: in the step 2, the size of the groove is formed by connecting equivalent section outlines of the groove into a plurality of line segments, and a group of sizes of chamfer circular arc transition is arranged at the position of an inflection point.
5. The AMESim-based mechanical transmission static gear shifting simulation method according to claim 4, wherein the AMESim-based mechanical transmission static gear shifting simulation method comprises the following steps:
in step 4, the spring parameters include initial installation pressure and stiffness of each spring.
6. The AMESim-based mechanical transmission static gear shifting simulation method according to claim 5, wherein the AMESim-based mechanical transmission static gear shifting simulation method comprises the following steps:
in the step 1, the simulation model is built by a mechanical library module in AMESim software.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110257756.4A CN113111449A (en) | 2021-03-09 | 2021-03-09 | Mechanical transmission static gear shifting simulation method based on AMESim |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110257756.4A CN113111449A (en) | 2021-03-09 | 2021-03-09 | Mechanical transmission static gear shifting simulation method based on AMESim |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN113111449A true CN113111449A (en) | 2021-07-13 |
Family
ID=76711723
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110257756.4A Pending CN113111449A (en) | 2021-03-09 | 2021-03-09 | Mechanical transmission static gear shifting simulation method based on AMESim |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113111449A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113901592A (en) * | 2021-12-09 | 2022-01-07 | 江苏中科朗恩斯车辆科技有限公司 | Method and device for designing contour curve of gear shifting groove of vehicle gear shifter |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20070260438A1 (en) * | 2006-05-08 | 2007-11-08 | Langer William J | Vehicle testing and simulation using integrated simulation model and physical parts |
| CN105354399A (en) * | 2015-12-14 | 2016-02-24 | 北京航空航天大学 | Multidisciplinary and reliable modeling method of hydraulic servo mechanism based on failure mechanism |
| WO2016197552A1 (en) * | 2015-06-08 | 2016-12-15 | 广东工业大学 | High-speed platform movement parameter self-tuning method based on model identification and equivalent simplification |
| CN110298073A (en) * | 2019-05-21 | 2019-10-01 | 南京理工大学 | The shift of integrated neural network and physical system model loads Dynamic Simulation Method |
| CN110309614A (en) * | 2019-07-09 | 2019-10-08 | 重庆大学 | A kind of synchronizer shift emulation mode |
-
2021
- 2021-03-09 CN CN202110257756.4A patent/CN113111449A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20070260438A1 (en) * | 2006-05-08 | 2007-11-08 | Langer William J | Vehicle testing and simulation using integrated simulation model and physical parts |
| WO2016197552A1 (en) * | 2015-06-08 | 2016-12-15 | 广东工业大学 | High-speed platform movement parameter self-tuning method based on model identification and equivalent simplification |
| CN105354399A (en) * | 2015-12-14 | 2016-02-24 | 北京航空航天大学 | Multidisciplinary and reliable modeling method of hydraulic servo mechanism based on failure mechanism |
| CN110298073A (en) * | 2019-05-21 | 2019-10-01 | 南京理工大学 | The shift of integrated neural network and physical system model loads Dynamic Simulation Method |
| CN110309614A (en) * | 2019-07-09 | 2019-10-08 | 重庆大学 | A kind of synchronizer shift emulation mode |
Non-Patent Citations (2)
| Title |
|---|
| 周召召: "商用车变速操纵机构换挡力学特性仿真研究", 《中国优秀硕士学位论文全文数据库 工程科技Ⅱ辑》, no. 08, 15 August 2015 (2015-08-15), pages 19 - 29 * |
| 王翔;刘武涛;龚尧平;: "汽车手动变速箱换挡力数学模型建立", 内燃机与配件, no. 08, 30 April 2019 (2019-04-30), pages 10 - 13 * |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113901592A (en) * | 2021-12-09 | 2022-01-07 | 江苏中科朗恩斯车辆科技有限公司 | Method and device for designing contour curve of gear shifting groove of vehicle gear shifter |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN113111449A (en) | Mechanical transmission static gear shifting simulation method based on AMESim | |
| CN103803011A (en) | Bicycle derailleur | |
| CN110238839A (en) | It is a kind of to optimize non-molding machine people multi peg-in-hole control method using environmental forecasting | |
| CN101508112A (en) | Acquisition method of three freedom-degree transportation industrial robot multiple-objective optimization design parameter | |
| CN101733750B (en) | Dynamic response spectrum-based method for planning track of robot with clearance at a joint | |
| CN107838934A (en) | It is a kind of can self-adapting grasping connecting rod under-actuated bionic finger | |
| CN102179818A (en) | Finger device of composite underactuated double-joint robot with differential-motion bevel gear system | |
| CN112613147B (en) | Simulation analysis method of mold locking mechanism and mold locking mechanism | |
| CN115990891B (en) | Robot reinforcement learning assembly method based on visual teaching and virtual-actual migration | |
| CN101901290A (en) | Machine design method based on three-dimensional virtual space of integrated mechanism | |
| CN204621641U (en) | Tool striking device | |
| CN105583829A (en) | Simulated mechanical finger pulled on basis of steel wire | |
| CN104965961A (en) | Speed changing box parking system simulation realization method based on plate spring flexible deformation | |
| CN109652927A (en) | Presser feet control method, device, computer equipment and storage medium | |
| CN205238062U (en) | Manipulator and robotic arm and robot | |
| Angerilli et al. | Haptic simulation of an automotive manual gearshift | |
| CN111686454A (en) | Multifunctional six-degree-of-freedom motion device | |
| CN206505585U (en) | A kind of multi-purpose type VR driver's cabs | |
| CN107403568A (en) | A kind of gear lever hangs shelves manipulation analogue means | |
| CN115327951A (en) | Three-degree-of-freedom control method for vehicle driving simulator and electronic equipment | |
| CN111751106A (en) | Gear shifting actuator testing device for AMT (automated mechanical transmission) | |
| CN206505586U (en) | A kind of universal VR driver's cabs gear shifting device | |
| CN208975176U (en) | Multiple degrees of freedom imaginary hinge turnover panel equipment based on Virtual Prototype Technique | |
| CN212389738U (en) | Selective-change execution unit limiting mechanism | |
| CN103029135A (en) | Muscle driving simulation robot joint |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |