CN112096852A - Method for designing gear shifting rule of automatic transmission with super-multi-gear - Google Patents
Method for designing gear shifting rule of automatic transmission with super-multi-gear Download PDFInfo
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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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/14—Inputs being a function of torque or torque demand
- F16H59/24—Inputs being a function of torque or torque demand dependent on the throttle opening
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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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/36—Inputs being a function of speed
- F16H59/44—Inputs being a function of speed dependent on machine speed of the machine, e.g. the vehicle
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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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/50—Inputs being a function of the status of the machine, e.g. position of doors or safety belts
- F16H59/54—Inputs being a function of the status of the machine, e.g. position of doors or safety belts dependent on signals from the brakes, e.g. parking brakes
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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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/60—Inputs being a function of ambient conditions
- F16H59/66—Road conditions, e.g. slope, slippery
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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
- F16H61/02—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 the signals used
- F16H61/0202—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 the signals used the signals being electric
- F16H61/0204—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 the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
- F16H61/0213—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 the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal characterised by the method for generating shift 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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/14—Inputs being a function of torque or torque demand
- F16H2059/142—Inputs being a function of torque or torque demand of driving resistance calculated from weight, slope, or the like
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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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/60—Inputs being a function of ambient conditions
- F16H59/66—Road conditions, e.g. slope, slippery
- F16H2059/663—Road slope
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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
- F16H61/02—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 the signals used
- F16H61/0202—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 the signals used the signals being electric
- F16H61/0204—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 the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
- F16H61/0213—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 the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal characterised by the method for generating shift signals
- F16H2061/0216—Calculation or estimation of post shift values for different gear ratios, e.g. by using engine performance tables
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Abstract
The invention discloses a method for designing a gear shifting rule of an automatic transmission with super-multi gears, and relates to the technical field of transmission control. The method comprises the four steps of obtaining human-vehicle-road system information, determining a target gear according to a dynamic speed ratio adjusting method by the vehicle speed and the accelerator opening, determining a current gradient highest gear according to the current system information, and taking a lower gear of the current gradient highest gear and the target gear as a final gear. The optimal dynamic property of the whole vehicle is taken as a design target, the gear shifting rule of the automatic transmission with the super-multi gear positions is designed, on the premise of ensuring the climbing performance of the vehicle, gear shifting is carried out near the maximum power point of an engine, so that the vehicle is ensured to have enough acceleration performance, the gear shifting types comprise sequential gear shifting, gear jumping and gear keeping, the automatic switching of the three gear shifting types can reduce the gear shifting times and the gear shifting loss, and the gear of the transmission can be ensured to change along with the vehicle speed in real time.
Description
Technical Field
The invention belongs to the technical field of transmission control, and particularly relates to a method for designing a gear shifting rule of an automatic transmission with multiple gears.
Background
Military vehicles often run in severe environment, and face steep slopes and continuous pothole pavements, a vehicle transmission system must provide enough traction force, and at the moment, a vehicle transmission is required to switch gears in real time according to road conditions, the more gears of the transmission are, the stronger the vehicle can adapt to the road conditions, and the working point of an engine can be improved. The continuously variable transmission can change the transmission ratio in real time according to road conditions, but the continuously variable transmission is weak in bearing capacity and low in working reliability and cannot be used for military vehicles with large load capacity and severe working environments, so that part of researchers propose a multi-gear automatic transmission, for example, an invention patent with the patent number of CN 106195157B discloses a multi-gear automatic transmission for vehicles, the transmission realizes 10 forward gears and 1 reverse gear through four planetary rows, and the current automatic transmission develops towards the trend of more gears.
For the multi-gear automatic transmission, the gear shifting process is relatively complex, sometimes, the vehicle needs to continuously shift gears in a short time, so that the clutch is in an incomplete engagement state for a long time, and the problems of serious power shortage, vehicle speed reduction and the like of the vehicle can be caused due to the fact that the clutch is in a friction state and transmission power of the transmission is blocked, so that the gear shifting rule of the multi-gear automatic transmission is relatively complex. Currently, the research on the gear shifting rules of multi-gear automatic transmissions is relatively few, most researchers are engaged in the research on the gear shifting rules of passenger vehicles or commercial vehicles, for example, the invention patent with the patent number of CN 110550034A discloses a two-gear AMT comprehensive gear shifting method for a pure electric vehicle, the method uses the speed and the gear shifting delay amount of a gear shifting point as optimization variables, uses the difference value between the energy consumption of the whole vehicle and the acceleration of the gear shifting point as a target function, and solves the gear shifting rules with comprehensive performance through an NSGA-II genetic algorithm.
The invention provides a method for designing a gear shifting rule of an automatic transmission with multiple gears, which takes the automatic transmission with multiple gears as a research object, considers the vehicle speed, the accelerator opening, the road gradient and the brake signal representing the information of a human-vehicle-road system when designing the gear shifting rule, and provides a gear shifting rule integrating gear shifting types such as sequential gear shifting, gear skipping, gear maintaining and the like, so that the practical vehicle applicability of the gear shifting rule can be obviously improved.
Disclosure of Invention
The invention aims to solve the technical problems that the gear shifting rule of an automatic transmission with multiple gears is complex, the gear shifting rule of a common transmission cannot be suitable for the automatic transmission with multiple gears and the like, and the gear shifting rule of the automatic transmission with multiple gears is designed on the basis of a dynamic speed ratio adjusting method, so that the gears of the transmission can be changed in real time according to road conditions, and the aim of optimal power performance of the whole vehicle is fulfilled.
In order to solve the technical problems, the invention is realized by adopting the following technical scheme: the method for designing the gear shifting rule of the automatic transmission with the super-multi gears is characterized by comprising the following steps of:
the method comprises the following steps that firstly, the super multi-gear automatic transmission obtains human-vehicle-road system information from the outside, specifically comprises vehicle speed, accelerator opening, road gradient and brake signals, and the four parameters are used as gear shifting parameters in a gear shifting rule of the super multi-gear automatic transmission;
and secondly, determining a target gear according to the vehicle speed and the accelerator opening degree and a dynamic speed ratio adjusting method, wherein the method specifically comprises the following steps:
firstly, calculating the engine rotating speed corresponding to the maximum engine power under each accelerator opening;
secondly, calculating the speed ratio of the transmission without limitation according to the relation between the engine speed and the vehicle speed as shown in the formula (1);
in the formula, the relationship between the accelerator opening degree and the engine speed may be represented by ne＝f(β)，neIs the engine speed, beta is the throttle opening, rwIs the wheel radius, i0Is the main reducer speed ratio, uaAs the vehicle speed, ioutAn unrestricted transmission ratio;
thirdly, the maximum and minimum speed ratio limitation is carried out on the speed ratio of the transmission which is not limited according to the speed ratio variation range of the automatic transmission with the super-multi gears, as shown in the formula (2)
In the formula imaxFor maximum speed ratio of automatic transmission with more than multiple gears, iminFor exceeding minimum speed ratio, i, of automatic multi-gear transmissionslimitIs the limited transmission ratio;
determining the speed variation range, drawing a two-dimensional table between the speed, the accelerator opening and the limited speed ratio of the transmission, determining the target speed ratio of the transmission by looking up the table according to the current speed and the accelerator opening, comparing the target speed ratio of the transmission with the corresponding speed ratio of each gear of the automatic transmission with the super-multi gear, and selecting the gear which is closest to each speed ratio of the automatic transmission with the super-multi gear as the target gear;
thirdly, determining the current gradient highest gear according to the current system information, and specifically comprising the following steps:
calculating the current engine speed according to the formula (1) by the vehicle speed and the current gear, and looking up a table by an engine Map according to the current engine speed and the current accelerator opening to obtain the current engine torque;
if no braking signal exists in the current man-vehicle-road system information, calculating the current gradient resistance, acceleration resistance, rolling resistance and air resistance according to the input man-vehicle-road system information, further calculating to obtain the driving force of the whole vehicle, specifically calculating as shown in formula (3), and then calculating to obtain the highest gear climbing up to the current gradient according to the driving force of the whole vehicle and the current engine torque, specifically calculating as shown in formula (4);
in the formula icurrentAs current road grade, FtAs a driving force of the entire vehicle, FfTo rolling resistance, FiAs slope resistance, FwAs air resistance, FjFor acceleration resistance, G is the vehicle weight, m is the vehicle mass, f1Is a coefficient of rolling resistance, CDThe coefficient is an air resistance coefficient, A is a windward area, u is a vehicle speed, is a rotating mass conversion coefficient, and a is a vehicle acceleration;
in the formula iiThe current grade highest gear is adopted, and T is the current engine torque;
if the current man-vehicle-road system information has a brake signal, calculating the current gradient resistance, acceleration resistance, rolling resistance and air resistance according to the input man-vehicle-road system information, further calculating to obtain the engine braking force, specifically calculating to obtain a highest gear of the current gradient according to the engine braking force and the current engine braking torque, specifically calculating to obtain a formula (6), and obtaining a relation between the current engine braking torque and the current engine rotating speed according to a formula (7);
in the formula, FbAs engine braking force, f2To take into account the rolling resistance coefficient of the ground braking force, and2＞f1；
in the formula, TbCurrent engine braking torque;
Tb＝ne·k (7)
in the formula, k is an engine braking proportional coefficient;
and fourthly, taking a lower gear from the highest gear of the current gradient and the target gear as a final gear, and taking the final gear as the current gear in the next gear shifting.
Compared with the prior art, the invention has the beneficial effects that:
1. the method for designing the gear shifting rule of the automatic transmission with the ultra-multiple gears takes the representative information of each component in a human-vehicle-road system as the gear shifting parameter, and corrects the double-parameter gear shifting rule of the vehicle speed and the accelerator opening degree through the road gradient and the brake signal, so that the actual running condition of the vehicle is better met;
2. the method for designing the gear shifting rule of the automatic transmission with the super-multi gears integrates the gear shifting types such as sequential gear shifting, gear jumping, gear keeping and the like, can reduce the gear shifting times, reduce the gear shifting loss and ensure that the gears of the transmission can change along with the vehicle speed in real time;
3. the method for designing the gear shifting rule of the automatic transmission with the super-multi gears shifts near the maximum power point of an engine, ensures the dynamic property of the whole vehicle, and improves the acceleration performance of the vehicle on the premise of ensuring the climbing capability of the vehicle.
Drawings
The invention is further described with reference to the accompanying drawings in which:
FIG. 1 is a schematic diagram of an automatic transmission with multiple gear positions according to the method for designing a gear shifting schedule of the automatic transmission with multiple gear positions of the present invention;
FIG. 2 is a flowchart of an overall method for designing a shift schedule for a super multi-speed automatic transmission according to the present invention;
FIG. 3 is a two-dimensional table of vehicle speed-accelerator opening-limited transmission speed ratios in a method of designing a gear shift schedule for a super multi-gear automatic transmission according to the present invention;
FIG. 4 is a graph illustrating target speed ratio changes of a transmission according to a method for designing a shift schedule of an automatic transmission with multiple gear positions according to the present invention;
fig. 5 is a relationship diagram between a target gear, a current gradient highest gear and a final gear in the method for designing the gear shifting law of the automatic transmission with multiple gears according to the present invention.
Detailed Description
In order to make the objects, contents and advantages of the present invention clearer, the following detailed description of the embodiments of the present invention will be made with reference to the accompanying drawings.
Referring to fig. 1, to solve the problems of the prior art, the present invention provides a method for designing a shift schedule of an automatic transmission with multiple gear positions, wherein the automatic transmission with multiple gear positions comprises a planetary line X, and a planetary line X, the planetary line X, and the planetary line X are forward gear planetary lines, the planetary line X is a reverse gear planetary line, the planetary line X comprises a sun gear S, a planetary gear P, a ring gear R, a planetary carrier CA, a brake C, and a clutch C, and the planetary line X comprises a sun gear S, The brake C7 and the clutch C8, the planet row X5 comprises a sun gear S5, planet gears P5, a gear ring R5, a planet carrier CA5, a brake C9 and a clutch C10, the planet row X6 comprises a sun gear S6, planet gears P6, a gear ring R6, a planet carrier CA6, a brake C11 and a clutch C12, all the planet rows are double internal meshing planet rows, and the planet gears in all the planet rows are meshed with the corresponding sun gear and gear ring in an internal meshing manner; the transmission power input end is connected with a ring gear R1 of a planetary row X1, a sun gear S1 of a planetary row X1 is connected with a sun gear S2 of a planetary row X2, a ring gear R2 of a planetary row X2 is connected with a sun gear S3 of a planetary row X3, a ring gear R3 of the planetary row X3 is connected with a sun gear S4 of the planetary row X4, a ring gear R4 of the planetary row X4 is connected with a sun gear S5 of a planetary row X5, a ring gear R5 of the planetary row X5 is connected with a planet carrier CA6 of a planetary row X6, and a sun gear S6 of the planetary row X6 is connected with the transmission power output end; by the cooperation of the brake and the clutch, two speed ratios can be formed by each planetary row, so that the automatic transmission with the multiple gears has 32 forward gears and 32 reverse gears.
Referring to fig. 2, a method for designing a gear shifting rule of an automatic transmission with multiple gears comprises the following specific processes:
the method comprises the following steps that firstly, the super multi-gear automatic transmission obtains human-vehicle-road system information from the outside, specifically comprises vehicle speed, accelerator opening, road gradient and brake signals, and the four parameters are used as gear shifting parameters in a gear shifting rule of the super multi-gear automatic transmission;
and secondly, determining a target gear according to the vehicle speed and the accelerator opening degree and a dynamic speed ratio adjusting method, wherein the method specifically comprises the following steps:
firstly, calculating the engine rotating speed corresponding to the maximum engine power under each accelerator opening;
secondly, calculating the speed ratio of the transmission without limitation according to the relation between the engine speed and the vehicle speed as shown in the formula (1);
in the formula, the relationship between the accelerator opening degree and the engine speed may be represented by ne＝f(β)，neIs the engine speed, beta is the throttle opening, rwIs the wheel radius, i0Is the main reducer speed ratio, uaAs the vehicle speed, ioutAn unrestricted transmission ratio;
thirdly, the maximum and minimum speed ratio limitation is carried out on the speed ratio of the transmission which is not limited according to the speed ratio variation range of the automatic transmission with the super-multi gears, as shown in the formula (2)
In the formula imaxFor maximum speed ratio of automatic transmission with more than multiple gears, iminFor exceeding minimum speed ratio, i, of automatic multi-gear transmissionslimitIs the limited transmission ratio;
fourthly, referring to the graph 3, determining the vehicle speed change range, and drawing a two-dimensional table of the vehicle speed, the accelerator opening and the limited transmission speed ratio;
referring to fig. 4, according to the vehicle speed and the accelerator opening at each moment, the target speed ratio of the transmission at each moment can be determined by looking up the two-dimensional table, then the target speed ratio of the transmission is compared with the corresponding speed ratio of each gear of the super multi-gear automatic transmission, and the gear corresponding to the speed ratio which is closest to the corresponding speed ratio of each gear of the super multi-gear automatic transmission is selected as the target gear;
thirdly, determining the current gradient highest gear according to the current system information, and specifically comprising the following steps:
calculating the current engine speed according to the formula (1) by the vehicle speed and the current gear, and looking up a table by an engine Map according to the current engine speed and the current accelerator opening to obtain the current engine torque;
if no braking signal exists in the current man-vehicle-road system information, calculating the current gradient resistance, acceleration resistance, rolling resistance and air resistance according to the input man-vehicle-road system information, further calculating to obtain the driving force of the whole vehicle, specifically calculating as shown in formula (3), and then calculating to obtain the highest gear climbing up to the current gradient according to the driving force of the whole vehicle and the current engine torque, specifically calculating as shown in formula (4);
in the formula icurrentAs current road grade, FtAs a driving force of the entire vehicle, FfTo rolling resistance, FiAs slope resistance, FwAs air resistance, FjFor acceleration resistance, G is the vehicle weight, m is the vehicle mass, f1Is a coefficient of rolling resistance, CDIs the coefficient of air resistance, A is the windward directionThe area, u is the vehicle speed, is the rotating mass conversion coefficient, and a is the vehicle acceleration;
in the formula iiThe current grade highest gear is adopted, and T is the current engine torque;
if the current man-vehicle-road system information has a brake signal, calculating the current gradient resistance, acceleration resistance, rolling resistance and air resistance according to the input man-vehicle-road system information, further calculating to obtain the engine braking force, specifically calculating to obtain a highest gear of the current gradient according to the engine braking force and the current engine braking torque, specifically calculating to obtain a formula (6), and obtaining a relation between the current engine braking torque and the current engine rotating speed according to a formula (7);
in the formula, FbAs engine braking force, f2To take into account the rolling resistance coefficient of the ground braking force, and2＞f1；
in the formula, TbCurrent engine braking torque;
Tb＝ne·k (7)
in the formula, k is an engine braking proportional coefficient;
referring to fig. 5, in the fourth step, a lower gear is selected from the current gradient highest gear and the target gear as a final gear, and the final gear is used as a current gear in the next gear shift; in 1-9 s in fig. 5, the final gear of the vehicle is always the target gear, but the final gear of the vehicle is limited by the climbing capability in the 10 th s and cannot follow the target gear any more, and the final gear of the vehicle is changed into the highest gear of the current gradient at the moment, namely the gear shifting rule of the automatic transmission with the super-multiple gear positions provided by the invention realizes the correction of the target gear and ensures the climbing capability of the vehicle; from the change condition of a final gear in a vehicle test process, the initial gear of the vehicle is 12 gears, the gear change sequence in the test process is 12-14-15-15-15-15-17-18-18-18, the gear shift process comprises three types of sequential gear shift, gear skip and gear maintenance, wherein the gear skip is mainly 2 gears in a continuous skip mode, the gear shift rule unifies the gear shift types of sequential gear shift, gear skip, gear maintenance and the like, the gear shift frequency is reduced, the gear shift loss is reduced, the gear of the transmission can be guaranteed to change along with the vehicle speed in real time, and the gear shift rule can be used as the gear shift rule of the automatic transmission with the super multi-gear.
Many other combinations and modifications of the shift parameters in the gearshift schedule of an automatic transmission with super-range gears are possible on the basis of the above description, and not exhaustive enumeration of all embodiments is possible, and obvious changes and modifications may be made without departing from the scope of the invention as defined in the claims and their equivalents.
Claims (1)
1. A method for designing a gear shifting rule of an automatic transmission with super-multi gears is characterized by comprising the following steps:
the method comprises the following steps that firstly, the super multi-gear automatic transmission obtains human-vehicle-road system information from the outside, specifically comprises vehicle speed, accelerator opening, road gradient and brake signals, and the four parameters are used as gear shifting parameters in a gear shifting rule of the super multi-gear automatic transmission;
and secondly, determining a target gear according to the vehicle speed and the accelerator opening degree and a dynamic speed ratio adjusting method, wherein the method specifically comprises the following steps:
firstly, calculating the engine rotating speed corresponding to the maximum engine power under each accelerator opening;
secondly, calculating the speed ratio of the transmission without limitation according to the relation between the engine speed and the vehicle speed as shown in the formula (1);
in the formula, the relationship between the accelerator opening degree and the engine speed may be represented by ne＝f(β)，neIs the engine speed, beta is the throttle opening, rwIs the wheel radius, i0Is the main reducer speed ratio, uaAs the vehicle speed, ioutAn unrestricted transmission ratio;
thirdly, the maximum and minimum speed ratio limitation is carried out on the speed ratio of the transmission which is not limited according to the speed ratio variation range of the automatic transmission with the super-multi gears, as shown in the formula (2)
In the formula imaxFor maximum speed ratio of automatic transmission with more than multiple gears, iminFor exceeding minimum speed ratio, i, of automatic multi-gear transmissionslimitIs the limited transmission ratio;
determining the speed variation range, drawing a two-dimensional table between the speed, the accelerator opening and the limited speed ratio of the transmission, determining the target speed ratio of the transmission by looking up the table according to the current speed and the accelerator opening, comparing the target speed ratio of the transmission with the corresponding speed ratio of each gear of the automatic transmission with the super-multi gear, and selecting the gear which is closest to each speed ratio of the automatic transmission with the super-multi gear as the target gear;
thirdly, determining the current gradient highest gear according to the current system information, and specifically comprising the following steps:
calculating the current engine speed according to the formula (1) by the vehicle speed and the current gear, and looking up a table by an engine Map according to the current engine speed and the current accelerator opening to obtain the current engine torque;
if no braking signal exists in the current man-vehicle-road system information, calculating the current gradient resistance, acceleration resistance, rolling resistance and air resistance according to the input man-vehicle-road system information, further calculating to obtain the driving force of the whole vehicle, specifically calculating as shown in formula (3), and then calculating to obtain the highest gear climbing up to the current gradient according to the driving force of the whole vehicle and the current engine torque, specifically calculating as shown in formula (4);
in the formula icurrentAs current road grade, FtAs a driving force of the entire vehicle, FfTo rolling resistance, FiAs slope resistance, FwAs air resistance, FjFor acceleration resistance, G is the vehicle weight, m is the vehicle mass, f1Is a coefficient of rolling resistance, CDThe coefficient is an air resistance coefficient, A is a windward area, u is a vehicle speed, is a rotating mass conversion coefficient, and a is a vehicle acceleration;
in the formula iiThe current grade highest gear is adopted, and T is the current engine torque;
if the current man-vehicle-road system information has a brake signal, calculating the current gradient resistance, acceleration resistance, rolling resistance and air resistance according to the input man-vehicle-road system information, further calculating to obtain the engine braking force, specifically calculating to obtain a highest gear of the current gradient according to the engine braking force and the current engine braking torque, specifically calculating to obtain a formula (6), and obtaining a relation between the current engine braking torque and the current engine rotating speed according to a formula (7);
in the formula, FbAs engine braking force, f2To take into account the rolling resistance coefficient of the ground braking force, and2＞f1；
in the formula, TbCurrent engine braking torque;
Tb＝ne·k (7)
in the formula, k is an engine braking proportional coefficient;
and fourthly, taking a lower gear from the highest gear of the current gradient and the target gear as a final gear, and taking the final gear as the current gear in the next gear shifting.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202011036184.9A CN112096852B (en) | 2020-09-27 | 2020-09-27 | Method for designing gear shifting rule of automatic transmission with super-multi-gear |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202011036184.9A CN112096852B (en) | 2020-09-27 | 2020-09-27 | Method for designing gear shifting rule of automatic transmission with super-multi-gear |
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| CN112744219A (en) * | 2020-12-29 | 2021-05-04 | 驭势科技（北京）有限公司 | Method and device for determining vehicle load |
| CN113007293A (en) * | 2021-03-09 | 2021-06-22 | 吉林大学 | Double-state double-inner-meshing planetary gear transmission structure |
| CN113389890A (en) * | 2021-07-28 | 2021-09-14 | 潍柴动力股份有限公司 | Method for determining climbing gear and related device |
| CN114321326A (en) * | 2021-12-30 | 2022-04-12 | 蜂巢传动科技河北有限公司 | Transmission structure of multi-gear automatic transmission, determination method, device and medium thereof |
| CN114684139A (en) * | 2022-03-30 | 2022-07-01 | 东风汽车集团股份有限公司 | Gear shifting control method and system based on intelligent driving |
| CN114704630A (en) * | 2022-04-24 | 2022-07-05 | 吉林大学 | Method for designing gear shifting rule of 32-gear two-state logic automatic transmission |
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