CN113847422B - Torque control method and system of AMT intermediate shaft brake - Google Patents
Torque control method and system of AMT intermediate shaft brake Download PDFInfo
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- CN113847422B CN113847422B CN202111112508.7A CN202111112508A CN113847422B CN 113847422 B CN113847422 B CN 113847422B CN 202111112508 A CN202111112508 A CN 202111112508A CN 113847422 B CN113847422 B CN 113847422B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H61/0437—Smoothing ratio shift by using electrical signals
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H2061/0012—Transmission control for optimising power output of driveline
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H2061/0068—Method or means for testing of transmission controls or parts thereof
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H2061/0075—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by a particular control method
- F16H2061/009—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by a particular control method using formulas or mathematic relations for calculating parameters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H2061/0459—Smoothing ratio shift using map for shift parameters, e.g. shift time, slip or pressure gradient, for performing controlled shift transition and adapting shift parameters by learning
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- Mechanical Engineering (AREA)
- Control Of Transmission Device (AREA)
- General Details Of Gearings (AREA)
Abstract
The invention discloses a torque control method and a torque control system of an AMT intermediate shaft brake.A whole vehicle experiment and a rack experiment are carried out under N given gear shifting working conditions to obtain N item standard speed curves and speed curves; obtaining a difference value between a target speed curve and a speed curve under the same given gear shifting working condition, and recording the quantity of lubricating oil and the clearance of a middle shaft brake assembly in a bench test when the difference value is smaller than a set threshold value; obtaining a transfer function equation or a comparison table of the current given gear shifting working condition according to the speed curve and the pressure curve of the cylinder piston under the current given gear shifting working condition; according to the invention, a speed curve can be obtained through the lookup table or the explicit function equation, and the speed curve can predict the gear shifting performance of the TB under a new gear shifting working condition, so that the accurate control of the torque transmission in the TB combining process can be realized by adjusting the determined lubricating oil quantity and the gap of the intermediate shaft brake assembly.
Description
Technical Field
The invention belongs to the technical field of gear shifting of a transmission, and particularly belongs to a method and a system for controlling the torque of an AMT intermediate shaft brake in a rapid gear shifting process.
Background
The AMT needs to adjust the rotating speed through an intermediate shaft brake (TB) in the quick gear shifting process, the TB uses a multi-plate wet clutch, and a pneumatic piston is combined with the multi-plate wet clutch to reduce the speed of the intermediate shaft. However, under different working conditions, the flow and temperature of lubricating oil, the position distribution of the friction plates of the separating plates, the initial position of the piston, the stress condition of the piston and the like are different, the same control strategy is adopted, the rotating speed reduction value of the intermediate shaft is different, and accurate control is difficult to achieve, so that the gear shifting smoothness and consistency are influenced, and the user experience is influenced. So during a shift, accurate control of torque transfer by TB is critical to the smoothness of the shift.
In the torque transmission process, the amount of lubricating oil and the thickness of an oil film have great influence on the torque transmission, but at present, no method for measuring the total amount of the lubricating oil flowing through the clutch assembly in the gear shifting process exists, and the amount of the lubricating oil needs to be calibrated in a bench test to realize the accuracy of torque transmission control;
the total clearance of the clutch plates is the moving distance of the piston in the combination process, when a single-body bench test and a whole-vehicle test are carried out, the clearances of the clutch assemblies obtained in the single-body bench test and the whole-vehicle test are different, the clearances of the clutch assemblies obtained in the single-body bench test for multiple times under the same working condition are different, the clearances of the clutch assemblies obtained in the whole-vehicle test for multiple times under the same working condition are different, and the torque performance curve obtained on the single-body bench test is inconsistent with the torque performance curve in the whole-vehicle test, so that the accuracy of torque transmission is influenced.
Disclosure of Invention
In order to solve the problems in the prior art, the invention provides a torque control method and a torque control system of an AMT intermediate shaft brake, which are used for judging and predicting a TB result process torque transmission rule and realizing the accurate control of TB combined process torque transmission, a single bench test is introduced to analyze the influence rule of the lubricating oil quantity of important influencing factors and the clearance of a wet clutch assembly on the torque transmission, an instructive suggestion is provided for the future development of TB, the development period can be effectively shortened, the development efficiency is improved, and the cost is reduced.
In order to achieve the purpose, the invention provides the following technical scheme: a torque control method of an AMT intermediate shaft brake comprises the following specific steps:
s1, determining lubricating oil temperature and cylinder piston pressure curve P (t, S) i ) Given N given shift conditions S i (i＝1,2,…,N)；
S2 under given gear shifting working condition S i Carrying out whole vehicle experiment under the condition to obtain N given gear shifting working conditions S i Corresponding N output shaft target speed curves Vel v (t,S i )；
S3, acquiring each given gear shifting working condition S i Amount of lubricating oil Q (S) under the conditions i,…,…,N ) And a clearance C (S) of the intermediate shaft brake assembly i,…,…,N ) Based on the obtained amount Q (S) of lubricating oil i,…,…,N ) And a clearance C (S) of the intermediate shaft brake assembly i,…,…,N ) Performing bench test to obtain N given gear shifting conditions S i Corresponding N output shaft speed curves Vel b (t,Si)；
S4, determining the same given gear shifting working condition S i Lower target speed curve Vel v (t,S i ) And velocity curve Vel b (t, si), when the difference is less than the set threshold, according to the current given gear shifting working condition S i Velocity profile Vel under the conditions b (t, si) vs. Cylinder piston pressure Curve P (t, S) i ) Obtaining the current given gear shifting working condition S i A transfer function equation or a look-up table;
s5, N given gear shifting working conditions S i Integrating a transfer function equation or a comparison table under the condition to obtain an explicit function equation or a query table;
s6, acquiring a speed curve Vel under a new working condition according to an explicit function equation or a lookup table TF (t, si), adjusting the velocity curve Vel TF (t, si) amount of lubricating oil Q (S) of intermediate shaft brake i,…,…,N ) And/or countershaft brake assembly clearance C (S) i,…,…,N ) And the control of the torque of the AMT intermediate shaft brake is realized.
Further, in step S3, the intermediate shaft brake assembly clearance C (S) i,…,…,N ) Is the nominal clearance of the intermediate shaft brake.
Further, in step S3, the amount Q (S) of the lubricating oil is set i,…,…,N ) The nominal amount of lubricating oil for the intermediate shaft brake.
Further, in step S4, a shift condition S is given i Output shaft target speed curve Vel under conditions v (t,S i ) And velocity curve Vel b The (t, si) difference is calculated as:
further, in step S4, if the difference is greater than the set threshold, the process returns to stepS3, adjusting the clearance C of the intermediate shaft brake assembly (S) i ) And/or the flow rate Q (S) of the lubricating oil i ) Up to the corresponding output shaft target speed curve Vel v (t,S i ) And velocity curve Vel b The difference of (t, si) is less than the set threshold.
Further, in step S4, when the difference is smaller than the set threshold, the current given gear shifting condition S is recorded i Under the condition, the intermediate shaft brake assembly clearance C (S) used in the bench test i ) And the amount Q (S) of lubricating oil i )。
Further, in step S4, the set threshold is 1% to 10%.
Further, in step S5, the explicit function equation or the look-up table is applied to the amount Q (S) of the lubricating oil i,…,…,N ) And a clearance C (S) of the intermediate shaft brake assembly i,…,…,N ) And (6) carrying out interpolation.
Further, in step S5, the input of the explicit function equation or the lookup table is the cylinder piston pressure curve P (t, S) i ) The output is the velocity curve Vel b (t,Si)。
The invention also provides a torque control method system of the AMT intermediate shaft brake, which comprises a finished automobile experiment device, a rack experiment device, a data processing device and a control adjusting device, wherein:
the whole vehicle experimental device is used for determining the temperature of lubricating oil and the pressure curve P (t, S) of the cylinder piston i ) Under given shift condition S i Carrying out whole vehicle experiment under the condition to obtain N given gear shifting working conditions S i Corresponding N output shaft target speed curves Vel v (t,S i )；
The bench experimental device is used for setting a gear shifting working condition S i According to the corresponding given gear shifting working condition S under the condition i Set amount of lubricating oil Q (S) i,…,…,N ) And a clearance C (S) of the intermediate shaft brake assembly i,…,…,N ) Performing bench test to obtain N given gear shifting conditions S i Corresponding N output shaft speed curves Vel b (t,Si)；
The data processing device is used for setting the same given gear shifting working condition S i Is as followsTarget speed curve Vel v (t,S i ) And velocity curve Vel b (t, si) are compared to obtain the current given gear shifting working condition S i Transfer function equation or look-up table, and giving N given shift conditions S i Integrating a transfer function equation or a comparison table under the condition to obtain an explicit function equation or a query table;
the control adjusting device is used for acquiring a speed curve Vel under a new working condition according to an explicit function equation or a lookup table TF Amount of lubricating oil Q (S) corresponding to (t, si) i,…,…,N ) And/or countershaft brake assembly clearance C (S) i,…,…,N ) Adjusting the amount Q (S) of lubricating oil in the intermediate shaft brake i,…,…,N ) And/or countershaft brake assembly clearance C (S) i,…,…,N ) And the control of the torque of the AMT intermediate shaft brake is realized.
Compared with the prior art, the invention at least has the following beneficial effects:
the invention provides a torque control method and a torque control system of an AMT intermediate shaft brake. In the process, through adjusting the lubricating oil quantity and the assembly clearance of the intermediate shaft brake in the process of changing different given gear shifting working conditions, the gear shifting process output shaft speed curves corresponding to different lubricating oil quantities and assembly clearances under the given gear shifting working condition conditions are obtained, a large number of given gear shifting working conditions, lubricating oil quantities, intermediate shaft brake assembly clearances and output shaft speed curves are abstracted to form a query table or an explicit function expression, the gear shifting performance of the TB in the gear shifting process under the new gear shifting working condition is predicted through the speed curves, and the gear shifting smoothness is improved to provide guiding opinions; according to the lubricating oil mass and/or the assembly clearance value of the intermediate shaft brake corresponding to the obtained speed curve, the lubricating oil mass entering the intermediate shaft brake and/or the assembly clearance of the intermediate shaft brake are/is adjusted, so that the accurate control of the torque transmission of the intermediate shaft brake is realized, and the smoothness and the consistency of gear shifting are realized;
meanwhile, the invention can avoid that the required lubricating oil quantity and assembly clearance of the intermediate shaft brake can be obtained only by bench experiments after the whole vehicle experiments are carried out under the new gear shifting working condition through the query table or the explicit function expression, can obtain the speed curve of the output shaft when the desired intermediate shaft brake is shifted through the query table or the explicit function expression directly, and provides guidance for improving the gear shifting smoothness by utilizing the speed curve prediction, thereby effectively shortening the development period, improving the development efficiency and reducing the cost.
Drawings
FIG. 1 is a schematic structural view of an intermediate shaft brake (TB);
FIG. 2 is a flowchart of a bench test for a given shift condition;
FIG. 3 is a flow chart of a multi-calibration forming look-up table or explicit transfer function equation;
in the drawings: 1. the brake comprises a brake piston, 2 parts of a top pin, 3 parts of a top cap, 4 parts of a brake cylinder cover, 5 parts of an air pipe, 6 parts of a friction plate, 7 parts of a separating plate, 8 parts of an intermediate shaft, 9 parts of a compression spring and 10 parts of a sealing ring.
Detailed Description
The invention is further described with reference to the following figures and detailed description.
As shown in fig. 1, the intermediate shaft brake has a simplified structure, and the main components are a piston 1, a friction plate 6, a separator 7, a compression spring 9, and the like. The friction plate 6 has friction material on both sides. The friction plates 6 are connected to the intermediate shaft 8 by internal splines, and the separator plates 7 are connected to the transmission housing (not labeled in fig. 1) by external splines. A certain gap exists between the friction plate 6 and the separating plate 7, and lubricating oil flows through the gap between the friction plate 6 and the separating plate 7 in the TB to form an oil film which transfers torque and dissipates heat for the TB. In the combination process, the gas pressure in the cylinder of the pneumatic piston 1 is increased, the resistance of the sealing ring 10, the spline friction force, the restoring force of the compression spring 9, the oil film resistance and the like are overcome, and the friction plate 6 and the separating plate 7 are pushed to be combined. In combination with the fact that a complete oil film exists between the friction plate 6 and the separation plate 7 at the initial stage, and because a rotation speed difference exists between the friction plate 6 and the separation plate 7, torque is completely transmitted through shearing of the oil film, and the quantity of lubricating oil and the thickness of the oil film have great influence on torque transmission in the process. As the distance between the friction plate 6 and the separator 7 is continuously reduced to be smaller than the surface roughness of the friction plate 6, the contact of the microprotrusions occurs, and coulomb friction occurs. At this time, a part of the torque is transmitted by the dimple contact, another part of the torque is transmitted by the fluid dynamics, and the relative rotational speed between the friction plate 6 and the separation plate 7 is further reduced. As the clearance is further reduced, the contact area of the friction plate 6 and the separator plate 7 is further increased, and all the torque is transmitted by friction, generating a large amount of heat, requiring continuous cooling of the lubricating oil. The temperature of the oil in the transmission is typically measured at the bottom sump, and this temperature can be used to specify the test temperature on bench tests. A temperature sensor may also be inserted into the clutch assembly to measure the temperature of the lubricating oil film between the friction plate and the separator plate. There is still no way to measure the total amount of oil that flows through the clutch assembly during a shift, so this amount of oil requires bench test calibration.
The total clutch plate clearance is the distance the piston moves during engagement. The torque performance obtained on the single test stand may be different from the torque curve in a full vehicle test, as the clearance or piston initial contact point of the clutch assembly may be different from that when on the full vehicle. Since, after the deceleration process is finished, the brake piston 1 is depressurized and the piston 1 returns to the initial position under the action of the compression spring 9, however, there is no measure to make the friction plates 6 and the separating plates 7 evenly distributed in the brake chamber, so the positions of the friction plates 6 and the separating plates 7 are random after each separation, which results in the inconsistency of the torque transmission during each combination process. The positions where the piston 1 initially contacts the separating plate 7 are different, and the distances between the friction plate 6 and the separating plate 7 are also different;
in summary, the present invention provides a torque control method for an AMT intermediate shaft brake, as shown in fig. 2 and 3, the specific steps are as follows:
step 2-1, in a given gear shifting working condition S i Under the conditions of obtainingThe curve of the rotating speed and the time of the output shaft in the TB combining process in the whole vehicle test is the target speed curve Vel of the output shaft in the given gear shifting working condition process on the bench test v (t,S i )。
Step 2-2, calibrating the clearance C of the intermediate shaft brake assembly (S) i ) Intermediate shaft brake assembly clearance C (S) i ) Is the nominal clearance of the intermediate shaft brake.
In step 2-3, the amount Q of lubricating oil flowing into the intermediate shaft brake is calibrated (S) i ) Amount of lubricating oil Q (S) i ) The nominal amount of lubricating oil for the intermediate shaft brake.
In step 2-4, the amount Q (S) of the lubricating oil is determined i ) And a clearance C (S) of the intermediate shaft brake assembly i ) Performing a torque bench test on the intermediate shaft brake to obtain a given gear shifting working condition S i Lower output shaft speed curve Vel b (t,Si)。
In step 2-5, calculating a given gear shifting condition S i Output shaft target speed curve Vel under conditions v (t,S i ) And velocity curve Vel b The difference between (t, si) is expressed by
If the difference is greater than the set threshold, then step 2-6 is entered, and the initial assembly clearance C is systematically adjusted (S) i ) And/or initial lube oil flow rate Q (S) i ) And (4) repeating the steps 2-4, 2-5 and 2-6 until the difference value of the two curves is smaller than the set threshold value.
If the difference is less than the set threshold, then step 2-7 is entered, and the initial transmission assembly clearance C used in the bench test is recorded (S) i ) And initial amount of lubricating oil Q (S) i )。
The value of the set threshold is 1% -10%, preferably 1% -5%.
In steps 2-8, according to the speed curve Vel b (t, si) and cylinder piston pressure curve P (t, S) i ) Obtaining a given working condition S i Correspondence of lower pressure curve and velocity curveThe relation is a transfer function equation or a comparison table, and the input is a cylinder piston pressure curve P (t, S) i ) The output is a speed profile.
in step 3-1, a given lubricating oil temperature, cylinder piston pressure curve P (t, S) is determined i ) At N given shift conditions S i (i =1,2, \8230;, N) N given shift conditions S are obtained by the method in step 2 i (i =1,2, \8230;, N) transfer function equations or look-up tables;
preferably, each given shift operating mode S i The clearance C (S) of the intermediate shaft brake assembly needs to be calibrated again at the lower part i ) And the amount Q (S) of lubricating oil i ) Different given shift conditions S i Corresponding to different intermediate shaft brake assembly clearances C (S) i ) And the amount Q (S) of lubricating oil i )。
And 3-2, integrating the intermediate shaft brake torque transfer function equations under the N different working conditions obtained in the step 3-1 into a lookup table or an explicit function equation.
Preferably, the look-up table or explicit function equation allows for different initial amounts of oil Q (S) i ) And initial amount of lubricating oil Q (S) i ) Interpolation is performed to cover all possible operating conditions over a wider area.
Preferably, since the temperature of the lubricating oil may also influence the shift behavior, this temperature can also be taken into account as a variable in the transfer function. This transfer function can be used to predict the shift behavior of TB during a shift under different operating conditions.
In step 3-3, in new M given shift conditions S i Then, the whole vehicle test and the bench test are not needed, and the transfer function interpolation (the lubricating oil quantity Q (S)) can be directly carried out i ) And/or countershaft brake assembly clearance C (S) i ) To obtain at M given shift regimes S i Velocity profile Vel TF (t, si), the velocity profile Vel TF (t, si) for predicting shift performance during a shift of TB; or from a control angleStarting from the starting point, if there is a predetermined target speed curve Vel v (t, si) whereby the transfer function can be used to reverse the desired amount of lubricating oil Q (S) i ) And/or countershaft brake assembly clearance C (S) i ) So that it is possible to follow the speed curve Vel TF Amount of lubricating oil Q (S) corresponding to (t, si) i ) To regulate the amount of lubricating oil flowing between the friction disk 6 and the separator disk 7 in the TB and/or according to the speed curve Vel TF Intermediate shaft brake assembly clearance C (S) corresponding to (t, si) i ) The gap between the friction plate 6 and the separating plate 7 in the intermediate shaft brake is adjusted, so that the torque transmission in the TB combining process is accurately controlled, and the gear shifting smoothness is realized.
In step 3-4, a bench test is performed on the velocity curve Vel obtained in step 3-3 TF (t, si) verification is carried out, and a test curve generated by a bench test and a speed curve Vel obtained by interpolation of a transfer function are obtained b The difference value of (t, si) is less than the set threshold value, which indicates that the test curve generated by the bench test and the velocity curve Vel obtained by the interpolation of the transfer function b (t, si) similarly, the velocity curve Vel is obtained in step 3-3 TF (t, si) may be used to predict shift behavior during a shift of TB.
According to the invention, a speed curve can be obtained through a lookup table or an explicit function equation, and the speed curve can predict the gear shifting performance of the TB under a new gear shifting working condition, so that the accurate control of the torque transmission in the TB combining process can be realized by adjusting the lubricating oil quantity and the gap of the intermediate shaft brake assembly.
Claims (8)
1. A torque control method of an AMT intermediate shaft brake is characterized by comprising the following specific steps:
s1, determining lubricating oil temperature and cylinder piston pressure curve P (t, S) i ) Given N given shift conditions S i (i＝1,2,…,N)；
S2 under the given gear shifting working condition S i Carrying out whole vehicle experiment under the condition to obtain N given gear shifting working conditions S i Corresponding N output shaft target speed curves Vel v (t,S i )；
S3, acquiring each given gear shifting working condition S i Amount of lubricating oil Q (S) under the conditions i,…,…,N ) And a clearance C (S) of the intermediate shaft brake assembly i,…,…,N ) Based on the obtained amount Q (S) of lubricating oil i,…,…,N ) And a clearance C (S) of the intermediate shaft brake assembly i,…,…,N ) Performing bench test to obtain N given gear shifting conditions S i Corresponding N output shaft speed curves Vel b (t,Si)；
S4, determining the same given gear shifting working condition S i Lower target speed curve Vel v (t,S i ) And velocity curve Vel b (t, si), when the difference is less than the set threshold, according to the current given gear shifting working condition S i Velocity profile Vel under conditions b (t, si) vs. Cylinder piston pressure Curve P (t, S) i ) Obtaining the current given gear shifting working condition S i A transfer function equation or look-up table;
s5, N given gear shifting working conditions S i Integrating a transfer function equation or a comparison table under the condition to obtain an explicit function equation or a query table;
s6, acquiring a speed curve Vel under a new working condition according to an explicit function equation or a look-up table TF (t, si), adjusting the speed curve Vel TF (t, si) of lubricating oil quantity Q (S) of intermediate shaft brake i,…,…,N ) And/or countershaft brake assembly clearance C (S) i,…,…,N ) The control of the torque of the AMT intermediate shaft brake is realized;
in step S4, if the difference value is larger than the set threshold value, the step S3 is returned to, and the clearance C of the intermediate shaft brake assembly is adjusted (S) i ) And/or the flow rate Q (S) of the lubricating oil i ) Up to the corresponding output shaft target speed curve Vel v (t,S i ) And velocity curve Vel b (t, si) is less than a set threshold;
the input of the explicit function equation or the look-up table is a cylinder piston pressure curve P (t, S) i ) The output is a speed curve Vel b (t,Si)。
2. The method of claim 1, wherein in step S3, the countershaft brake assembly clearance C (S) is provided i,…,…,N ) Is the nominal clearance of the intermediate shaft brake.
3. The method of claim 1, wherein in step S3, said amount of lubricating oil Q (S) is set as i,…,…,N ) The nominal amount of lubricating oil for the intermediate shaft brake.
4. The method of claim 1, wherein in step S4, a shift condition S is given i Output shaft target speed curve Vel under conditions v (t,S i ) And velocity curve Vel b The (t, si) difference is calculated as:
5. the method for controlling the torque of an AMT intermediate shaft brake as recited in claim 1, wherein in step S4, when the difference is less than the set threshold, the current given shift condition S is recorded i Under the condition, the intermediate shaft brake assembly clearance C (S) used in the bench test i ) And the amount Q (S) of lubricating oil i )。
6. The method for controlling the torque of the AMT intermediate shaft brake as recited in claim 1, wherein in the step S4, the set threshold is 1% -10%.
7. The method of claim 1, wherein in step S5, the explicit function equation or look-up table is applied to the amount Q (S) of lubricating oil i,…,…,N ) And a clearance C (S) of the intermediate shaft brake assembly i,…,…,N ) And (6) carrying out interpolation.
8. The utility model provides a torque control system of AMT jackshaft stopper which characterized in that, includes whole car experimental apparatus, rack experimental apparatus, data processing device, control adjusting device, wherein:
the whole vehicle experimental device is used for determining the temperature of lubricating oil and the pressure curve P (t, S) of the cylinder piston i ) Under given shift condition S i Carrying out whole vehicle experiment under the condition to obtain N given gear shifting working conditions S i Corresponding N output shaft target speed curves Vel v (t,S i )；
The bench test device is used for determining the temperature of lubricating oil and the pressure curve P (t, S) of the cylinder piston i ) Under given shift condition S i According to the corresponding given gear shifting working condition S under the condition i Set amount of lubricating oil Q (S) i,…,…,N ) And a clearance C (S) of the intermediate shaft brake assembly i,…,…,N ) Performing bench test to obtain N given gear shifting conditions S i Corresponding N output shaft speed curves Vel b (t,Si)；
The data processing device is used for setting the same given gear shifting working condition S i Lower target speed curve Vel v (t,S i ) And velocity curve Vel b (t, si) are compared to obtain the current given gear shifting working condition S i Transfer function equation or look-up table, and giving N given shift conditions S i Integrating a transfer function equation or a comparison table under the condition to obtain an explicit function equation or a query table;
the control adjusting device is used for acquiring a speed curve Vel under a new working condition according to an explicit function equation or a look-up table TF Amount of lubricating oil Q (S) corresponding to (t, si) i,…,…,N ) And/or countershaft brake assembly clearance C (S) i,…,…,N ) Adjusting the quantity Q (S) of lubricating oil in the intermediate shaft brake i,…,…,N ) And/or countershaft brake assembly clearance C (S) i,…,…,N ) The control of the torque of the AMT intermediate shaft brake is realized;
the input of the explicit function equation or the look-up table is a cylinder piston pressure curve P (t, S) i ) The output is the velocity curve Vel b (t,Si)。
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| CN115031019B (en) * | 2022-07-04 | 2024-07-30 | 一汽解放汽车有限公司 | Brake control method, device, controller and medium |
| CN115388834B (en) * | 2022-08-26 | 2024-08-13 | 博世华域转向系统有限公司 | Intermediate shaft looseness gap detection and early warning method for electric power steering system |
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| US5393274A (en) * | 1993-07-19 | 1995-02-28 | Eaton Corporation | Touch point identification algorithm for automatic clutch controller |
| CN101566203B (en) * | 2009-05-11 | 2011-02-02 | 湘潭大学 | Intermediate shaft brake of hydraulic retarding type automatic speed changer |
| CN102269678B (en) * | 2011-05-13 | 2013-01-30 | 重庆蓝黛动力传动机械股份有限公司 | Testing device for temperature measurement of wet multi-plate clutch friction steel disc |
| US9512889B2 (en) * | 2013-04-30 | 2016-12-06 | Ford Global Technologies, Llc | Control of a transmission friction element using an adaptive transfer function |
| CN104297148B (en) * | 2014-10-28 | 2017-01-18 | 扬州大学 | Lubricated friction feature measurement and analysis system and operating method thereof |
| CN206017674U (en) * | 2016-08-18 | 2017-03-15 | 中国第一汽车股份有限公司 | A kind of New Brake |
| CN210087868U (en) * | 2018-09-26 | 2020-02-18 | 陕西法士特齿轮有限责任公司 | AMT jackshaft braking structure that shifts in step |
| CN109163031B (en) * | 2018-09-26 | 2024-01-02 | 陕西法士特齿轮有限责任公司 | AMT jackshaft braking structure |
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