Intelligent testing method for high-horsepower full-power gear shifting tractor

Abstract

The present application relates to the field of tractor testing technology, and more particularly to a method for testing intelligent large-horsepower full-power gear shifting tractors, which comprises the following steps: synchronously collecting clutch oil filling pressure, output shaft torque, output shaft speed and gearbox oil temperature, and constructing a synchronous data sequence with a unified time reference; for any time, calculating the rate of change of the clutch oil filling pressure and performing a negative exponential operation on the amplitude of the output shaft torque drop to obtain a decay coefficient, and then obtaining a power coupling index; determining characteristic time points and mechanical synchronous time points, and calculating response time lag and speed synchronization deviation, and obtaining a phase alignment index through logarithmic operation of the product; weighting and fusing the power coupling index and the phase alignment index and performing temperature correction to obtain a comprehensive score for determining the quality level. The present application reflects the quality of the gear shifting process through the measurement of amplitude cooperation and time sequence alignment, and reduces the interference of environmental factors on the test.

Description

Technical Field

[0001] This invention relates to the field of tractor testing technology, and in particular to an intelligent testing method for high-horsepower, all-power shift tractors. Background Technology

[0002] The transmission system of high-horsepower all-power shift tractors usually adopts an all-power shift gearbox to cope with complex working conditions. In order to ensure the smoothness and structural reliability of the transmission system during shifting transients, establishing an intelligent testing method that can accurately reflect dynamic physical characteristics plays a key role in improving the overall operating efficiency of the machine.

[0003] Existing testing methods mostly employ discrete-time data sampling, acquiring pressure and speed signals by placing sensors on the gearbox and output shaft. At the signal processing level, algorithms such as low-pass filtering are typically used to reduce noise in the raw electrical signals, obtain the pressure peak or speed drop value that characterizes the shift quality, and evaluate the performance level of the shift process in conjunction with preset static thresholds.

[0004] However, traditional evaluation methods have limitations when dealing with the nonlinear dynamic process of full-power shifting, which involves millisecond-level energy conversion. Due to the complex physical coupling between the pressure build-up process at the actuator end and the torque fluctuations at the power load end on the time axis, existing discrete-point sampling models cannot effectively calculate the dynamic matching relationship between the execution intensity and load feedback at each moment. Considering that the oil filling characteristics of the hydraulic system are affected by changes in transmission oil temperature, fluctuations in the viscosity-temperature characteristics of the oil can cause uncertainties in the pressure response time. Since conventional evaluation models are mostly based on static parameters and lack adaptive correction logic for oil temperature environment and system efficiency deviations, the test results obtained under different temperature conditions exhibit significant dispersion. This deviation in phase alignment between the execution action and the power response makes it difficult for the test system to accurately capture the microscopic slippage or transient energy loss caused by response time delay, further reducing the probability of accurately evaluating the shift smoothness of the transmission system. Summary of the Invention

[0005] To address the technical problems of inaccurate evaluation during full-power shifting due to the lack of dynamic coupling between execution and load, and the deviation in response phase caused by environmental temperature interference, this invention provides an intelligent testing method for high-horsepower full-power shifting tractors. This method includes the following steps:

[0006] The system synchronously collects clutch filling pressure, output shaft torque, output shaft speed, and transmission oil temperature from the tractor's transmission to construct a synchronous data sequence with a unified time reference. For any moment in the synchronous data sequence, the rate of change of the clutch filling pressure is calculated, and the decrease in output shaft torque at the corresponding moment is obtained. A negative exponential operation is performed on the decrease in output shaft torque to obtain an attenuation coefficient. Based on the rate of change of the clutch filling pressure and the attenuation coefficient, the power coupling index for each moment is obtained. The system determines the characteristic moment when the clutch filling pressure reaches a preset engagement threshold and the mechanical synchronization moment when the output shaft speed reaches the target speed. The response time delay between the characteristic moment and the mechanical synchronization moment is calculated, and the speed synchronization deviation within the response time delay is obtained. A logarithmic operation is performed on the product of the response time delay and the speed synchronization deviation to obtain the phase alignment index for each moment. The power coupling index and the phase alignment index are weighted and fused to obtain a benchmark score. The temperature difference between the transmission oil temperature and the preset optimal oil temperature is calculated, and a temperature correction is performed on the benchmark score based on the temperature difference to obtain a comprehensive score to determine the quality level of the shifting process.

[0007] This invention establishes a data sequence with a unified time reference by synchronously collecting key physical quantities such as clutch filling pressure and output shaft torque. Considering the complex coupling relationship between the pressure build-up characteristics of the actuator and the load feedback of the power end during dynamic evolution, this invention calculates the rate of change of clutch filling pressure and evaluates the power coupling index at each moment by combining it with the torque drop amplitude. Furthermore, it calculates the response time delay and obtains the speed synchronization deviation by combining characteristic moment points and mechanical synchronization moment points, realizing a multi-dimensional measurement of amplitude matching and phase synchronization during gear shifting. It also introduces a transmission oil temperature correction coefficient to compensate for the environmental conditions of the evaluation results, effectively suppressing the inconsistency of test results caused by fluctuations in oil viscosity-temperature characteristics, and reducing the test accuracy deviation caused by asynchronous sampling or static evaluation modes of sensors. This provides an evaluation benchmark with a physical causal relationship for the performance judgment of gear shifting quality of high-horsepower tractors.

[0008] Preferably, the dynamic coupling index satisfies the following relationship:

[0009] ;

[0010] in, yes Dynamic coupling index at any given moment; yes The rate of change of clutch fill pressure at any given time represents the clutch fill pressure. Regarding time The first derivative; The coupling coefficient; yes The magnitude of the decrease in output shaft torque at any given moment; yes The preset target torque requirement at any given time; It is the preset first minute value; It is a natural exponential function.

[0011] This invention establishes a negative exponential mapping relationship between the rate of change of clutch filling pressure and the magnitude of the decrease in output shaft torque, and uses an attenuation coefficient to nonlinearly constrain the pressure build-up rate at the actuator end. This is used to evaluate the coordination level between the actuator's action intensity and the power chain feedback amplitude in the dynamic process, reducing the evaluation error caused by simply focusing on instantaneous peak values ​​while ignoring the physical continuity of the power connection process.

[0012] Preferably, the phase alignment index satisfies the following relationship:

[0013] ;

[0014] in, yes Phase alignment index at any given moment; yes The characteristic time point of time; yes The mechanical synchronization point of time; yes Constant output shaft speed synchronization deviation; It is the sensitivity balance factor; It is the preset second minute value; It is the natural logarithm function.

[0015] This invention couples the timing lag characteristics with the speed dimension misalignment characteristics by calculating the product of the response delay time and the speed synchronization deviation and performing logarithmic operations. This enhances the sensitivity of the evaluation results in capturing small phase shifts at the synchronization moment, and plays a role in accurately describing the synchronization stability of the phase control link.

[0016] Preferably, the step of calculating the response delay time between the characteristic time point and the mechanical synchronization time point, and obtaining the speed synchronization deviation within the response delay time, includes: obtaining data from the characteristic time point to the mechanical synchronization time point in the synchronization data sequence, denoted as the deviation calculation interval; calculating the difference between the target speed and the output shaft speed corresponding to each sampling point within the deviation calculation interval, extracting the maximum difference, and obtaining the speed synchronization deviation at each time point.

[0017] This invention extracts the maximum difference within the deviation calculation interval to focus on evaluating the most unfavorable slip condition generated during gear shifting, ensuring that the speed synchronization deviation can truly reflect the synchronization phase quality during the power switching phase, and reducing the probability of dynamic feature loss due to sampling discreteness.

[0018] Preferably, the step of weightedly fusing the dynamic coupling index and the phase alignment index to obtain a benchmark score includes: performing a nonlinear mapping on the dynamic coupling index using a preset normalization factor to obtain a mapping result; recording the ratio of the phase alignment index to a preset maximum reference value of the phase alignment index as the phase alignment ratio; and using preset weighting coefficients to perform a weighted summation of the mapping result and the phase alignment ratio to obtain the benchmark score.

[0019] This invention maps physical evaluation quantities of different dimensions to a controlled benchmark score space by performing nonlinear mapping on the dynamic coupling index and introducing a phase alignment ratio for weighted summation, thereby reducing the problem of inaccurate comprehensive evaluation caused by the inconsistency of the dimensions of multiple source indexes.

[0020] Preferably, the nonlinear mapping is implemented using the hyperbolic tangent function.

[0021] Preferably, the comprehensive score satisfies the following relationship:

[0022] ;

[0023] in, yes A comprehensive score for each moment; yes The baseline score at any given time; yes Transmission oil temperature at any given time; This is the optimal oil temperature; yes The efficiency compensation coefficient at any given time is obtained by querying a preset efficiency mapping table; It is a preset maximum score; It is the natural exponential function; It is the absolute value symbol.

[0024] This invention introduces an environmental correction layer consisting of transmission oil temperature and efficiency compensation coefficient. Taking into account the impact of oil temperature changes on hydraulic volumetric efficiency, the benchmark score is dynamically corrected, thereby reducing the negative impact of environmental factors on the robustness of test results.

[0025] Preferably, determining the quality level of the gear shifting process includes: acquiring a preset pass threshold and a warning threshold, wherein the pass threshold is greater than the warning threshold; when the comprehensive score is continuously greater than or equal to the pass threshold, the quality level of the gear shifting process is determined to be passable; when the comprehensive score is continuously less than the warning threshold, the quality level of the gear shifting process is determined to be abnormal.

[0026] Preferably, the construction of a synchronized data sequence with a unified time reference includes: using a unified sampling clock signal, setting a preset sampling frequency, and synchronously collecting the clutch filling pressure, output shaft torque, output shaft speed, and transmission oil temperature; aligning and associating the data of the clutch filling pressure, output shaft torque, and output shaft speed with the same timestamp as a reference, and arranging them in chronological order to obtain a synchronized data sequence with a unified time reference.

[0027] Preferably, the calculation of the rate of change of the clutch filling pressure includes: determining the shift activation time interval, which is the time interval from the moment the shift command is obtained to the moment when the output shaft speed reaches the target speed; calculating the derivative of the clutch filling pressure with respect to time at each moment within the shift activation time interval to obtain the rate of change of the clutch filling pressure.

[0028] The beneficial effects of this invention are as follows: By establishing a strict alignment correlation between multi-source sensor signals on the time axis, this invention solves the problem of distorted test results caused by timing misalignment between the pressure establishment at the execution end and the torque feedback at the power end. By acquiring power coupling and phase alignment indices, this invention enables the evaluation of the execution intensity and load response during gear shifting in terms of amplitude matching and phase synchronization, overcoming the shortcomings of traditional evaluation methods in characterizing dynamic matching relationships. Furthermore, by introducing a transmission oil temperature correction coefficient and an efficiency compensation mapping table, this invention effectively suppresses the interference of oil viscosity-temperature characteristic fluctuations on test accuracy, reduces the dispersion of test scores under different operating environments, and provides reliable evaluation data for optimizing the shifting smoothness of high-horsepower tractors. Attached Figure Description

[0029] Figure 1 A flowchart of the intelligent testing method for a high-horsepower full-power shift tractor provided in an embodiment of the present invention;

[0030] Figure 2 An efficiency mapping table provided for embodiments of the present invention;

[0031] Figure 3 This is a schematic diagram of indicator collaborative monitoring provided in an embodiment of the present invention;

[0032] Figure 4 This is a schematic diagram of the comprehensive scoring provided for an embodiment of the present invention. Detailed Implementation

[0033] This invention provides an intelligent testing method for high-horsepower, full-power shift tractors, such as... Figure 1 As shown, the method includes steps S100-S400:

[0034] Step S100: Synchronously collect the clutch filling pressure, output shaft torque, output shaft speed and gearbox oil temperature of the tractor gearbox to construct a synchronous data sequence with a unified time reference.

[0035] It should be noted that the intelligent testing of the full-power shifting process involves the synchronous monitoring of multiple physical quantities, such as clutch filling pressure, output shaft torque, and output shaft speed. Considering that clutch filling pressure characterizes the pressure build-up characteristics of the actuator, output shaft torque characterizes the shifting impact of the power load, and output shaft speed characterizes the synchronization phase of the mechanical transmission, collecting this data provides a foundational support for subsequent performance evaluation. Since shifting transients involve millisecond-level pressure pulsations and speed drops, if the acquisition points of these physical quantities are not accurately aligned on the time axis, it will lead to phase distortion in the subsequent calculation of the causal relationship between the pressure and power response feedback at the actuator. Therefore, this invention constructs a synchronous data sequence with a unified time reference through a high sampling rate link, ensuring that the action commands at the actuator and the response feedback at the power end have strict physical synchronization within the same clock sequence.

[0036] Specifically, a pressure sensor is placed at the gearbox control valve of the tractor under test, and a torque sensor and a speed sensor are placed at the gearbox output shaft. Using a unified sampling clock signal and setting the sampling frequency to 1000Hz, the sensor channels are synchronously triggered to collect the clutch filling pressure, output shaft torque, and output shaft speed at various times. The physical quantity data collected by each channel are aligned and correlated based on the same timestamp, and arranged in chronological order to obtain a synchronous data sequence representing the entire gear shifting process. A zero-phase digital filtering algorithm is used to perform noise reduction processing on the original signal to ensure that the filtered signal does not produce phase shift in the time domain, thereby completely preserving the transient characteristics of pressure and torque changes.

[0037] At this point, the synchronous data sequence of the gear shifting process has been obtained.

[0038] Step S200: For any moment in the synchronous data sequence, calculate the rate of change of the clutch oil filling pressure, obtain the decrease in the output shaft torque at the corresponding moment, perform a negative exponential operation on the decrease in the output shaft torque to obtain the attenuation coefficient, and obtain the power coupling index at each moment based on the rate of change of the clutch oil filling pressure and the attenuation coefficient.

[0039] It should be noted that the impact during full-power shifting is not determined solely by a single momentary peak value, but rather by the degree of coordination between the change in clutch filler pressure and the output shaft torque during the dynamic evolution of the shift. Considering that the matching of the shifting powertrain in the amplitude dimension directly affects the quality of the tractor's power delivery, dynamically mapping the rate of clutch filler pressure build-up to the proportion of output shaft torque decrease serves to evaluate the control algorithm's real-time ability to suppress shifting impact.

[0040] First, calculate the rate of change of clutch filling pressure.

[0041] It should be noted that during the dynamic process of clutch piston oil filling and engagement, the rate of increase in clutch oil pressure directly reflects the tightness of friction plate engagement. By calculating its first derivative, it not only characterizes the response strength of the actuator at the moment of gear shifting, but also reflects the speed at which the hydraulic system establishes engagement force.

[0042] Specifically, to acquire the synchronization data sequence, the shift activation time interval is first determined. This interval refers to the continuous process from the moment the control system issues the shift command until the output shaft speed reaches the speed corresponding to the target gear. Then, data within this shift activation time interval is acquired, and the clutch oil filling pressure at each moment is calculated in relation to time. The derivative of the value is used to obtain the rate of change of the clutch oil pressure at each moment.

[0043] Then, calculate the decrease in output shaft torque.

[0044] It should be noted that the decrease in output shaft torque directly reflects the mechanical shock caused by power interruption or uneven shifting, making it a core physical indicator for evaluating transmission smoothness. Therefore, by assessing the deviation between the target required value and the measured value, the degree of power interruption during gear shifting can be captured.

[0045] Specifically, the output shaft torque at each moment in the synchronous data sequence is obtained; simultaneously, the load torque expectation command issued in real time by the electronic control unit in the tractor control bus is obtained. The target torque required at any given time reflects the ideal steady-state output value preset by the system under the current gear, engine speed, and pedal opening. The difference between the target torque required and the collected output shaft torque is calculated to determine... The decrease in output shaft torque at the corresponding moment.

[0046] Finally, the dynamic coupling index is calculated.

[0047] It should be noted that the physical essence of shift quality lies in whether the actuation strength of the hydraulic end and the load feedback of the mechanical end are in a steady-state balance. Simply building up pressure quickly without considering torque loss can easily lead to strong transmission system oscillations. In order to capture the micro-matching mismatch of the powertrain under complex operating conditions, this invention uses a natural exponential function to construct an evaluation model based on negative feedback logic. The rate of change of clutch filling pressure is used as the basic gain, and the torque reduction ratio is used to nonlinearly suppress this gain, thereby achieving a comprehensive measurement of the connection quality of the power switching process.

[0048] Based on the above logic, the stated The dynamic coupling index at time t satisfies the following relationship:

[0049] ;

[0050] in, yes Dynamic coupling index at any given moment; yes The rate of change of clutch fill pressure at any given time represents the clutch fill pressure. Regarding time The first derivative; It is the coupling coefficient; yes The magnitude of the decrease in output shaft torque at any given moment; yes The target torque requirement at any given moment; It is a preset first tiny value used to prevent The value should be 0, preferably 0.001; It is a natural exponential function.

[0051] In this relation, Described The response strength of the actuator at any given moment; exponential term The proportion of output shaft torque reduction relative to the target torque demand was calculated using nonlinear mapping, thus dynamically constraining the rate of change of clutch filling pressure: when As the torque fluctuation ratio increases, this value decreases rapidly, thus suppressing... The value is used to characterize the state of the power chain at this time. The amplitude coordination capability at different times is poor.

[0052] It should be noted that the nonlinear coupling coefficient The value of needs to be set according to the thermal stability of the clutch friction material and the requirements for shift smoothness: for materials whose friction coefficient is more sensitive to changes in oil temperature, it is preferable to set it to 1.25 to 1.5 to enhance the penalty for torque fluctuations; for high-performance friction plates with good thermal stability, it is preferable to set it to 0.8 to 1 to maintain the sensitivity to capture small power fluctuations. In this embodiment, The preferred value is 1.15.

[0053] Thus, the dynamic coupling indices at each moment were obtained.

[0054] Step S300: Determine the characteristic moment when the clutch filling pressure reaches the preset engagement threshold and the mechanical synchronization moment when the output shaft speed reaches the target speed. Calculate the response time delay between the characteristic moment and the mechanical synchronization moment, obtain the speed synchronization deviation within the response time delay, and perform a logarithmic operation on the product of the response time delay and the speed synchronization deviation to obtain the phase alignment index at each moment.

[0055] It should be noted that the quality of power transition during full-power shifting depends on the alignment accuracy between the hydraulic system's pressure build-up completion moment and the mechanical transmission synchronization moment. This invention evaluates the synchronization capability of the phase control link in timing by calculating the phase difference duration and the accompanying speed deviation at the actuator, thus revealing the accuracy bottleneck of the control logic at the clock alignment level.

[0056] First, phase feature time is extracted.

[0057] It should be noted that the clutch filling pressure reaching the engagement threshold indicates that the hydraulic circuit has completed filling and entered the slippage critical point, while the output shaft speed reaching the target gear speed indicates that the physical synchronization of the power transmission path is complete. By extracting these two characteristic moments, a complete dynamic time chain from the hydraulic actuator's action to the mechanical response's feedback can be established, providing a benchmark for evaluating synchronization deviations.

[0058] Specifically, the synchronous data sequence is acquired to locate the characteristic moments when the clutch oil pressure reaches the preset engagement threshold. Simultaneously, identify the mechanical synchronization point at which the output shaft speed signal reaches the target speed. It should be noted that the preset engagement threshold value needs to be set according to the physical structural parameters of the clutch: for heavy-duty transmission units using high-stiffness return springs, to ensure accurate identification of the physical starting point of the piston pressing against the friction plate, it can preferably be set to 0.7 to 0.9 MPa; for ordinary transmission units with smaller return spring preload, to avoid misjudging the residual pressure of the system as the engagement starting point, it can preferably be set to 0.3 to 0.5 MPa. In this embodiment, the preset engagement threshold is preferably set to 0.5 MPa.

[0059] Then, the synchronization phase deviation is calculated.

[0060] It should be noted that the speed fluctuations generated during the execution lag not only reflect the energy loss due to slippage during gear shifting, but are also directly related to the dynamic load impact on the transmission system. Therefore, by obtaining the instantaneous speed deviation at the mechanical synchronization point, the degree of dynamic misalignment of the powertrain during phase loss of control can be accurately described.

[0061] Specifically, obtain the synchronous data sequence from the characteristic time point arrive The data at the specified location is used to calculate the difference between the target rotational speed and the actual collected output shaft rotational speed at each sampling point within the interval, and the maximum difference is extracted to obtain the output shaft rotational speed synchronization deviation at each time point.

[0062] Finally, the phase alignment index is calculated.

[0063] It should be noted that the physical evaluation of phase alignment needs to consider not only the absolute time difference, but also the cumulative effect of speed fluctuations. A simple time delay cannot distinguish the shift quality at different speeds. This invention utilizes a natural logarithmic mapping mechanism, coupling the time deviation and speed deviation through a product, to nonlinearly amplify minute phase perturbations in logarithmic space, thereby achieving a highly sensitive measurement of synchronization link stability.

[0064] Based on the above logic, the stated The phase alignment index at time t satisfies the following relationship:

[0065] ;

[0066] in, yes Phase alignment index at any given moment; yes The characteristic time point of time; yes The mechanical synchronization point of time. yes The shift response time at any given moment; yes Constant output shaft speed synchronization deviation; It is the sensitivity balance factor; It is a preset second tiny value used to prevent The value should be 0, preferably 0.001; It is the natural logarithm function.

[0067] In this relationship, the denominator describes the cumulative synchronization phase deviation generated during the delay time through a product, while the numerator is the sensitivity balance factor. It provides a benchmark for adjusting the evaluation weights. (Through...) The structure implements a nonlinear inversion mapping between evaluation scores and physical deviations: when Response time delay at any moment The closer to the theoretical response extreme value and the smaller the speed deviation, the smaller the value of the denominator term, leading to... The increase in the value reflects the control link in It maintains a high level of synchronization at all times.

[0068] It should be noted that the sensitivity balance factor The value needs to be set according to the rated speed of the transmission and the severity of the shift response: for heavy-duty models with high rated speed and high sensitivity to shift delay, it is preferred to set it to 2.2 to 2.8 rad to improve the capture accuracy of small phase misalignments; for medium- and low-speed operations and scenarios with high tolerance for smoothness, it is preferred to set it to 1.2 to 1.8 rad to avoid drastic fluctuations in the evaluation score caused by sensor sampling noise. In this embodiment, The preferred setting is 2 rad.

[0069] At this point, the phase alignment index for each moment has been obtained.

[0070] Step S400: The power coupling index and the phase alignment index are weighted and fused to obtain a benchmark score. The temperature difference between the transmission oil temperature and the preset optimal oil temperature is calculated. The benchmark score is corrected according to the temperature difference to obtain a comprehensive score to determine the quality level of the shifting process.

[0071] It should be noted that in actual testing environments, the robustness of test data can be affected by fluctuations in transmission oil temperature and drift in system volumetric efficiency. This invention introduces an adaptive compensation layer to map multi-dimensional indicators to a controlled scoring space, thereby eliminating physical errors caused by environmental viscosity-temperature characteristics and restoring the true performance level of the control system.

[0072] First, calculate the baseline score.

[0073] It should be noted that the comprehensive evaluation model needs to simultaneously consider the amplitude characteristics of dynamic coupling and the timing characteristics of phase alignment. By constructing a benchmark score free from environmental interference, the underlying logic performance of the control algorithm under ideal operating conditions can be intuitively reflected. Furthermore, the hyperbolic tangent function is used to nonlinearly limit the input index, preventing score overflow.

[0074] Specifically, the dynamic coupling index and the phase alignment index at each time step are combined and fused using a weighted average. Based on the above logic, the... The baseline score at time point satisfies the following relationship:

[0075] ;

[0076] in, yes The baseline score at any given time; It is the hyperbolic tangent function; It is a normalization factor; yes Dynamic coupling index at any moment These are its weighting coefficients; yes Phase alignment index at time. These are its weighting coefficients; It is the maximum reference value of the preset phase alignment index.

[0077] In this relation, the hyperbolic tangent function will The dynamic coupling index at any given moment is mapped to a finite interval, ensuring that the evaluation score remains numerically stable under high-intensity pressure build-up impact; weighting coefficients and By prioritizing the adjustment of the coupling degree of the power chain and the synchronization timing deviation, a comprehensive measurement of the multi-dimensional performance of the control algorithm is achieved.

[0078] It should be noted that the weighting coefficients , and normalization factor The value needs to be set according to the performance preference of the transmission: for comfort-oriented algorithm tests that focus more on shift smoothness, the optimal setting can be selected. It ranges from 0.6 to 0.7. The value is between 0.3 and 0.4; for competitive or high-frequency operation scenarios where response time is more critical, a more optimal setting can be selected. It is 0.4. It is 0.6. Normalization factor. The value of needs to be set according to the pressure build-up characteristics of the transmission hydraulic system and the evaluation resolution requirements: For heavy-duty transmissions with fast hydraulic system response and large change rate of clutch filling pressure, in order to prevent the evaluation score from entering the saturation region of the hyperbolic tangent function too early at a high slope, it is preferable to use Set it to a smaller size, such as to s / Pa, to maintain the analytical capability for extreme operating conditions; for conventional transmission systems with relatively smooth pressure build-up or low response intensity, in order to effectively distinguish the slight performance differences under different control logics, it is preferable to use s / Pa. Set it to a larger size, such as to s / Pa, to enhance the score's sensitivity to pressure fluctuations. In this embodiment, Preferred setting s / Pa.

[0079] Then, obtain the real-time environmental compensation parameters.

[0080] It should be noted that the viscosity of transmission fluid decreases with increasing temperature, causing a non-linear shift in the filling rate and internal leakage of the fluid transmission system. To ensure physical comparability of test scores under different environmental conditions, an environmental correction operator needs to be introduced to calibrate the original evaluation indicators.

[0081] Specifically, the measured transmission oil temperature at various times is obtained through temperature sensors placed inside the transmission. Meanwhile, according to such Figure 2 The preset efficiency mapping table shown uses the clutch filling pressure and output shaft speed at each moment to calculate the efficiency compensation coefficient under the current operating condition. The numerical relationships in the efficiency mapping table reflect the physical characteristics of the transmission system: as the clutch filling pressure increases, the internal leakage of the system increases, resulting in a negative correlation trend in the volumetric efficiency coefficient; as the output shaft speed increases, the dynamic volumetric performance of the system's oil supply components improves, resulting in a positive correlation trend in the efficiency coefficient. In practical applications, the grid density of this table can be increased according to the controller's storage space. For operating points located between grid nodes, this invention uses a bilinear interpolation algorithm to fit the data of four adjacent nodes to calculate the specific efficiency compensation coefficient at each moment. This dynamic mapping mechanism can effectively eliminate the nonlinear interference caused by operating condition fluctuations on the test results.

[0082] Finally, a comprehensive score is calculated and a performance assessment is performed.

[0083] It should be noted that the baseline score only represents performance under ideal conditions and must be weighted and corrected based on actual environmental parameters to truly measure the equipment's effective work capacity under current operating conditions. Dynamically penalizing the score through a temperature sensitivity index attenuation term can guide the test results back to the standard operating temperature range.

[0084] Based on the above logic, the stated The overall score at any given time satisfies the following relationship:

[0085] ;

[0086] in, yes A comprehensive score for each moment; yes The baseline score at any given time; yes Transmission oil temperature at any given time; This is the optimal oil temperature; yes Efficiency compensation coefficient at any given moment; The preset full score is 100 in this embodiment, but the implementer can set it according to the requirements. It is the natural exponential function; It is the absolute value symbol.

[0087] In this relation, The nonlinear decay is performed based on the physical distance of the current oil temperature from the optimal point, which helps to eliminate interference caused by non-standard environments and ensures that the final score is robust over time.

[0088] It should be noted that the maximum reference value for the phase alignment index is... and optimal oil temperature The value needs to be set according to the test accuracy requirements and the characteristics of the transmission medium: for precision transmission systems that pursue ultimate dynamic synchronization performance. It can be preferably set to 7 to 9 to provide a higher score resolution; for conventional heavy-duty power machinery, it can be preferably set to 4 to 6. This needs to be determined based on the viscosity-temperature characteristic curve of the hydraulic oil in the transmission to ensure that the system is in the optimal volumetric efficiency range, which can preferably be set to 75 to 85 degrees Celsius. In this embodiment, The preferred value is set to 5. The preferred setting is 80 degrees Celsius.

[0089] Specifically, a preset grading threshold is set, and the calculated comprehensive score at each time point is compared with the grading threshold; if If the result remains above the acceptable threshold, the intelligent test result for the current full-power shifting process is deemed acceptable; if... If the value is below the warning threshold, an abnormal performance alarm signal will be output.

[0090] It should be further noted that the values ​​of the pass threshold and the warning threshold need to be set according to the severity of the task: With a preset full score of 100, for high-precision applications such as new machine performance calibration, the pass threshold can be preferably set to 90 to 95 points to eliminate control logic with slight response deviations; for routine maintenance or general reliability and health monitoring, it can be preferably set to 75 to 85 points. The warning threshold is usually determined based on fault boundary statistics, aiming to identify critical states of significant power loss, and can be preferably set to 55 to 65 points. In this embodiment, the pass threshold is preferably set to 85 points, and the warning threshold is preferably set to 65 points; implementers can adjust these values ​​according to their needs.

[0091] like Figure 3 As shown in the figure, this is a schematic diagram of indicator coordination monitoring. The horizontal axis represents the number of sampling points, the left axis corresponds to the power coupling indicator, and the right axis corresponds to the phase alignment indicator. During the sampling point range of 800-1100, the solid line shows a peak, reflecting the response intensity of the rapid pressure build-up of the actuator; while the dashed line shows a deep dip between 800 and 1800, characterizing a significant response lag and speed deviation during gear shifting. This trend captures the nonlinear dynamic characteristics of energy conversion involved in gear shifting, providing a core physical basis for evaluating the quality of power connection.

[0092] like Figure 4 As shown, this graph is a schematic diagram of the comprehensive scoring. The horizontal axis represents the number of sampling points, and the vertical axis represents the comprehensive score. The pass / fail standard line is the curve corresponding to the pass threshold, and the warning threshold line is the curve corresponding to the warning threshold. Observation Figure 4 It can be seen that during the non-shifting steady-state periods of 0-800 and 1800-2500 RPM, the comprehensive score remains stable above 90 points, within the acceptable range, indicating that the system operates smoothly. However, during the shifting transient period from 800 to 1800 RPM, due to the combined effects of power coupling fluctuations and phase deviations, the green line rapidly drops to approximately 45 points, far below the warning threshold, triggering an abnormal alarm signal from the system. This demonstrates that after eliminating environmental interference such as oil temperature, this invention can reliably identify transient energy losses caused by response time delays, achieving accurate judgment of shifting quality.

[0093] This completes the intelligent testing process for the high-horsepower, all-power shift tractor.

[0094] The above are all preferred embodiments of the present invention and are not intended to limit the scope of protection of the present invention. Therefore, all equivalent changes made in accordance with the structure, shape and principle of the present invention should be covered within the scope of protection of the present invention.

Claims

1. A smart testing method for high-horsepower, full-power shift tractors, characterized in that: include: Synchronously collect clutch filling pressure, output shaft torque, output shaft speed and transmission oil temperature of tractor gearbox to construct a synchronous data sequence with a unified time base; For any moment in the synchronous data sequence, calculate the rate of change of the clutch filling pressure, obtain the decrease in the output shaft torque at the corresponding moment, perform a negative exponential operation on the decrease in the output shaft torque to obtain the attenuation coefficient, and obtain the power coupling index at each moment based on the rate of change of the clutch filling pressure and the attenuation coefficient. The characteristic moment when the clutch filling pressure reaches the preset engagement threshold and the mechanical synchronization moment when the output shaft speed reaches the target speed are determined. The response time delay between the characteristic moment and the mechanical synchronization moment is calculated. The speed synchronization deviation within the response time delay is obtained. Logarithmic operation is performed on the product of the response time delay and the speed synchronization deviation to obtain the phase alignment index at each moment. The power coupling index and the phase alignment index are weighted and fused to obtain a benchmark score. The temperature difference between the transmission oil temperature and the preset optimal oil temperature is calculated. The benchmark score is then corrected based on the temperature difference to obtain a comprehensive score to determine the quality level of the shifting process.

2. The intelligent testing method for high-horsepower full-power shift tractors according to claim 1, characterized in that, The dynamic coupling index satisfies the following relationship: ； in, yes Dynamic coupling index at any given moment; yes The rate of change of clutch fill pressure at any given time represents the clutch fill pressure. Regarding time The first derivative; The coupling coefficient; yes The magnitude of the decrease in output shaft torque at any given moment; yes The preset target torque requirement at any given time; It is the preset first minute value; It is a natural exponential function.

3. The intelligent testing method for high-horsepower full-power shift tractors according to claim 1, characterized in that, The phase alignment index satisfies the following relationship: ； in, yes Phase alignment index at any given moment; yes The characteristic time point of time; yes The mechanical synchronization point of time; yes Constant output shaft speed synchronization deviation; It is the sensitivity balance factor; It is the preset second minute value; It is the natural logarithm function.

4. The intelligent testing method for high-horsepower full-power shift tractors according to claim 1, characterized in that, The calculation of the response time delay between the characteristic moment point and the mechanical synchronization moment point, and the acquisition of the speed synchronization deviation within the response time delay, includes: Obtain the data from the characteristic time point to the mechanical synchronization time point in the synchronization data sequence, and denote it as the deviation calculation interval; Calculate the difference between the target rotational speed and the output shaft rotational speed at each sampling point within the deviation calculation interval, extract the maximum difference, and obtain the rotational speed synchronization deviation at each time point.

5. The intelligent testing method for high-horsepower full-power shift tractors according to claim 1, characterized in that, The weighted fusion of the dynamic coupling index and the phase alignment index to obtain the benchmark score includes: The mapping result is obtained by performing a nonlinear mapping on the dynamic coupling index using a preset normalization factor; The ratio of the phase alignment index to the preset maximum reference value of the phase alignment index is denoted as the phase alignment ratio. The mapping result and the phase alignment ratio are weighted and summed using preset weighting coefficients to obtain a benchmark score.

6. The intelligent testing method for high-horsepower full-power shift tractors according to claim 5, characterized in that, The nonlinear mapping is achieved using the hyperbolic tangent function.

7. The intelligent testing method for high-horsepower full-power shift tractors according to claim 1, characterized in that, The comprehensive score satisfies the following relationship: ； in, yes A comprehensive score for each moment; yes The baseline score at any given time; yes Transmission oil temperature at any given time; This is the optimal oil temperature; yes The efficiency compensation coefficient at any given time is obtained by querying a preset efficiency mapping table; It is a preset maximum score; It is a natural exponential function; It is the absolute value symbol.

8. The intelligent testing method for a high-horsepower, full-power shift tractor according to claim 1, characterized in that, The determination of the quality level of the gear shifting process includes: Obtain a preset qualified threshold and a warning threshold, wherein the qualified threshold is greater than the warning threshold; When the overall score is consistently greater than or equal to the passing threshold, the quality level of the gear shifting process is determined to be passing. When the overall score is consistently below the warning threshold, the quality level of the gear shifting process is determined to be abnormal.

9. The intelligent testing method for a high-horsepower, full-power shift tractor according to claim 1, characterized in that, The construction of a synchronized data sequence with a unified time base includes: Using a unified sampling clock signal and a preset sampling frequency, the clutch filling pressure, output shaft torque, output shaft speed and gearbox oil temperature are synchronously collected. The data on clutch filling pressure, output shaft torque, and output shaft speed are aligned and associated using the same timestamp as a reference, and arranged in chronological order to obtain a synchronized data sequence with a unified time reference.

10. The intelligent testing method for a high-horsepower, full-power shift tractor according to claim 1, characterized in that, The calculation of the rate of change of the clutch filling pressure includes: Determine the shift activation time interval, which is the time period from the moment the shift command is obtained until the moment the output shaft speed reaches the target speed; Calculate the first derivative of the clutch oil pressure with respect to time at each moment within the shift activation time interval to obtain the rate of change of the clutch oil pressure.

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