CN114018576B - Equivalent test method and system for real vehicle dynamic load stand of transmission device - Google Patents
Equivalent test method and system for real vehicle dynamic load stand of transmission device Download PDFInfo
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M13/00—Testing of machine parts
- G01M13/02—Gearings; Transmission mechanisms
- G01M13/027—Test-benches with force-applying means, e.g. loading of drive shafts along several directions
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M13/00—Testing of machine parts
- G01M13/02—Gearings; Transmission mechanisms
- G01M13/021—Gearings
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M17/00—Testing of vehicles
- G01M17/007—Wheeled or endless-tracked vehicles
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Abstract
The invention relates to the technical field of bench tests, and discloses a method and a system for equivalent test of a real-vehicle dynamic load bench of a transmission device. Firstly, carrying out real vehicle torque test on a transmission device carrying vehicle to obtain a torque test signal; preprocessing a torque test signal to obtain a real vehicle dynamic load and a transmission input rotating speed; dividing according to the actual vehicle dynamic load according to gears to obtain dynamic load courses corresponding to each gear; dividing the transmission input rotating speed into sections according to the dynamic load process corresponding to each gear to obtain a rotating speed section; calculating damage rates of an output gear and an output shaft of the transmission device according to the dynamic load process and the rotating speed interval; and determining dynamic loading torque and equivalent loading time of the set gear in the set rotating speed range by taking the obtained damage rate as a constraint condition, and carrying out a bench equivalent test. The invention can equivalently convert the dynamic load of the real vehicle and improve the pertinence and the effectiveness of the durability assessment of the transmission device.
Description
Technical Field
The invention relates to the technical field of bench tests, in particular to an equivalent test method and an equivalent test system for a real-vehicle dynamic load bench of a transmission device.
Background
The conventional bench durability test of the tracked vehicle transmission device mainly adopts a method of combining different gears, different input rotating speeds, different loading torques and different loading times, the conventional bench test of the transmission device usually adopts a motor as power, the dynamic characteristics of an engine are difficult to accurately simulate through the motor on a transmission test bench, and the test method of fixed rotating speed, fixed torque and fixed time has limited durability test effect on the transmission device.
The transmission device generally transmits power through rotating parts such as gears and shafts, damage of the gears can be measured through transmission torque and rotation times, and damage of shaft parts is generally measured through statistics of alternating torque amplitude-frequency of action in a rain flow counting mode. The fatigue acceleration test of the transmission usually only pays attention to the damage of gear parts, and pays less attention to the damage of shaft parts. The fixed rotating speed-fixed torque test method using the motor as power is less in damage effect on shaft parts of the transmission device due to the lack of alternating torque load, and the durability of the shaft parts cannot be effectively checked in the test and examination of the durability of the whole transmission device.
The lack of an equivalent loading method for the current durability assessment dynamic load leads to the fact that products passing the bench test often cannot pass the durability test on a real vehicle. Because the multi-cylinder engine has high-frequency variable torsional vibration characteristics and the motor equipment of the rack cannot effectively track the amplitude and frequency of the dynamic load of the real vehicle, a method must be found to select proper loading torque characteristics according to the performance of the rack loading equipment, the damage rates of the gear and the transmission shaft are achieved simultaneously in the whole machine test, and the aim of equivalent damage of the dynamic load of the real vehicle on the rack loading is fulfilled.
Disclosure of Invention
The invention aims to solve the technical problems in the prior art and provides a method and a system for equivalent test of a real-vehicle dynamic load rack of a transmission device, which can be used for equivalently converting the real-vehicle dynamic load and improving the pertinence and the effectiveness of the durability assessment of the transmission device.
In order to solve the problems, the invention adopts the following technical scheme:
the invention provides a method for testing the equivalent of a real-vehicle dynamic load stand of a transmission device, which comprises the following steps:
carrying out real vehicle torque test on a transmission device carrying vehicle to obtain a torque test signal;
preprocessing a torque test signal to obtain a real vehicle dynamic load and a transmission input rotating speed;
dividing according to the actual vehicle dynamic load according to gears to obtain dynamic load courses corresponding to each gear;
dividing the transmission input rotating speed into sections according to the dynamic load process corresponding to each gear to obtain a rotating speed section;
calculating damage rates of an output gear and an output shaft of the transmission device according to the dynamic load process and the rotating speed interval;
and determining dynamic loading torque and equivalent loading time of the set gear in the set rotating speed range by taking the obtained damage rate as a constraint condition, and carrying out a bench equivalent test.
Further, calculating the damage rate of the output shaft specifically includes:
the average value and the amplitude of the dynamic load of the real vehicle are respectively and evenly divided into k and h intervals, a rain flow matrix of h rows and k columns is constructed, and the dynamic load amplitude S is obtained a And dynamic load mean S m The corresponding number of cycles n ij (s a ,s m )；
According to the S-N curve of the shaft part, fatigue life conversion is carried out, and an equal-life curved surface C of the output shaft is obtained as shown in a formula (1):
wherein S is a S is the ith dynamic load amplitude in the rain flow matrix m For the j-th column dynamic load mean value, sigma in the rain flow matrix c The fracture strength of the shaft material is that N is the number of times of circulation, m and c are constants;
converting the formula (1) to obtain a dynamic load amplitude S a And dynamic load mean S m Corresponding maximum number of cycles N ij (s a ,s m ) I is 1 to h, j is 1 to k;
calculating to obtain the damage rate D of the output shaft shaft As shown in formula (2):
further, calculating the damage rate of the output gear specifically includes:
the damage rate D of fatigue dangerous parts of the output gear under the random load g As shown in formula (4):
wherein n is p For loading torque T corresponding to fatigue fracture test p Is actually rotated for a period of time, N p S-N curve for output gearCorresponding to the loading torque T p Maximum number of rotations of b and C 1 The gear material parameter is K, and K is a constant;
the formula (4) is simplified to be shown as a formula (5), wherein p takes a value of 1-q, and the loading torque transmitted by the output gear along the axial direction is divided into q equal parts from the minimum value to the maximum value:
further, the dynamic loading torque T load Formula (6) shows:
T load ＝T m +T a sin(ω·t) (6)
wherein T is m The dynamic load average value corresponding to the set gear in the set rotating speed interval is adopted as the dynamic torque average value; t (T) a For the dynamic torque amplitude, the dynamic torque average value T is set m 10% -20% of (a); t is equivalent loading time and is determined by the damage number of the output gear; ω is the loading frequency.
The invention also provides an equivalent test system of the real-vehicle dynamic load stand of the transmission device, which comprises:
torque test module: the torque testing device is used for carrying out real vehicle torque testing on the transmission device carrying vehicle to obtain a torque testing signal;
and a pretreatment module: the torque testing device is used for preprocessing the torque testing signal to obtain the dynamic load and the transmission input rotating speed of the real vehicle;
the gear dividing module is used for: the dynamic load process corresponding to each gear is obtained by dividing according to the dynamic load of the real vehicle and the gears;
the interval dividing module: the transmission input rotating speed is divided into intervals according to the dynamic load process corresponding to each gear to obtain a rotating speed interval;
the damage calculation module: the damage rate is calculated according to the dynamic load process and the rotating speed interval and the output gear and the output shaft of the transmission device;
and an equivalent test module: and the method is used for determining the dynamic loading torque and the equivalent loading time of the set gear in the set rotating speed range by taking the obtained damage rate as a constraint condition, and carrying out a bench equivalent test.
Further, the damage calculation module comprises a shaft damage calculation module and a gear damage calculation module.
Compared with the prior art, the invention has the beneficial effects that:
1. the invention provides an equivalent test method for a real-vehicle dynamic load table frame of a transmission device, which overcomes the defect that a motor is used as a power fixed rotating speed and fixed torque test method to damage shaft parts of the transmission device.
2. The invention adopts the damage rate D of the output shaft shaft And the damage number D of the output gear gear For constraint conditions, proper dynamic loading torque and equivalent loading time can be selected according to the performance of the rack loading equipment, so that the damage rates of the output gear and the output shaft in the complete machine test are ensured to be simultaneously achieved, the aim of equivalent damage of the dynamic load of the real vehicle in the rack loading is fulfilled, and the pertinence and the comprehensiveness in the complete machine test are improved.
3. The invention is based on equivalent damage, finds out a fatigue acceleration test method in the whole machine bench test, finds out a theoretical basis of dynamic load equivalent of the whole machine bench test, and effectively improves the scientificity of dynamic load loading equivalent of the bench.
Drawings
In order to more clearly illustrate the solution of the present invention, a brief description will be given below of the drawings required for the description of the embodiments, it being obvious that the drawings in the following description are some embodiments of the present invention, and that other drawings may be obtained from these drawings without inventive effort for a person skilled in the art. Wherein:
FIG. 1 is a flow chart of an equivalent test method for a real vehicle dynamic load carrier of a transmission device of the present invention.
FIG. 2 is a flow chart of the present invention for calculating the damage rate of the output shaft.
Fig. 3 is a schematic diagram of an equivalent test system for a real vehicle dynamic load carrier of the transmission device of the present invention.
Detailed Description
Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs; the terms used in the specification are used herein for the purpose of describing particular embodiments only and are not intended to limit the present invention, for example, the orientations or positions indicated by the terms "length", "width", "upper", "lower", "left", "right", "front", "rear", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. are orientations or positions based on the drawings, which are merely for convenience of description and are not to be construed as limiting the present invention.
The terms "comprising" and "having" and any variations thereof in the description of the invention and the claims and the description of the drawings above are intended to cover a non-exclusive inclusion; the terms first, second and the like in the description and in the claims or in the above-described figures, are used for distinguishing between different objects and not necessarily for describing a sequential or chronological order. In the description of the invention and the claims and the above figures, when an element is referred to as being "fixed" or "mounted" or "disposed" or "connected" to another element, it can be directly or indirectly on the other element. For example, when an element is referred to as being "connected to" another element, it can be directly or indirectly connected to the other element.
Furthermore, references herein to "an embodiment" mean that a particular feature, structure, or characteristic described in connection with the embodiment may be included in at least one embodiment of the present invention. The appearances of such phrases in various places in the specification are not necessarily all referring to the same embodiment, nor are separate or alternative embodiments mutually exclusive of other embodiments. Those of skill in the art will explicitly and implicitly appreciate that the embodiments described herein may be combined with other embodiments.
Referring to fig. 1, an embodiment of the invention provides a method for testing equivalent of a dynamic load stand of a transmission device for a real vehicle, which comprises the following steps:
step S1: and performing real vehicle torque test on the transmission device-mounted vehicle to obtain a torque test signal.
Step S2: and preprocessing the torque test signal to obtain the dynamic load and the transmission input rotating speed of the real vehicle.
In the above, as the equivalent transformation is carried out on the dynamic load of the real vehicle, the real vehicle torque test is carried out on the vehicle carried by the transmission device through the statistical analysis on the frequency spectrum characteristics of the real vehicle engine and ground excitation, the noise in the torque test signal is filtered by adopting a wavelet analysis method, the dynamic load of the real vehicle and the transmission input rotating speed output by the transmission device in the torque test signal are obtained, and the foundation is laid for the calculation of the damage rate of the subsequent rain flow count. The torque test signal is used for evaluating the damage degree of the output shaft and the output gear in the load time process.
Step S3: and dividing according to the dynamic load of the real vehicle and the gear to obtain a dynamic load process corresponding to each gear.
In the step, parameters such as torque, transmission input rotation speed and the like are divided according to gears according to real vehicle dynamic load data, and dynamic load histories corresponding to all gears (including forward gears, reverse gears and central steering gears) of a transmission device are obtained through statistics, so that a bench test scheme is formulated for each gear later.
Step S4: and dividing the transmission input rotating speed into sections according to the dynamic load process corresponding to each gear to obtain a rotating speed section.
In the step, after the dynamic load of the real vehicle is segmented according to the gears, each gear is divided into sections according to the transmission input rotating speed, and 4 to 5 sections are evenly divided between the lowest stable rotating speed of the engine and the highest statistical rotating speed.
Step S5: and calculating damage rates of an output gear and an output shaft of the transmission device based on the rain flow counting method according to the dynamic load process and the rotating speed interval, and obtaining the corresponding shaft damage rate and gear damage number of each gear in the set rotating speed interval.
In the step, as a certain dynamic association relation exists in the gear shaft system of the transmission device, the damage rate is calculated for the output gear and the output shaft of the transmission device respectively, and the subsequent dynamic load equivalent loading of the rack is taken as a constraint condition according to the calculated damage rate.
Step S6: determining dynamic loading scheme of rack, namely corresponding shaft damage rate D in corresponding rotation speed interval of each gear shaft And gear damage number D gear And (3) determining dynamic loading torque and equivalent loading time of the equivalent test of the bench for constraint conditions, and performing the equivalent test of the bench. Specifically, an amplitude value loading scheme is adopted, and relevant parameters such as transmission input rotating speed, an average value of dynamic loading torque, amplitude, loading frequency and the like are mainly combined to obtain dynamic loading torque and equivalent loading time under the condition of corresponding transmission input rotating speed under the specific gear condition, so that the determination of a rack equivalent test scheme is completed.
Further, referring to fig. 2, in step S5, the damage rate of the output shaft is calculated, which specifically includes the following steps:
step S511: uniformly dividing the average value of the dynamic load of the real vehicle into k intervals according to a rain flow counting method, uniformly dividing the amplitude value of the dynamic load of the real vehicle into h, counting to obtain a rain flow matrix of h rows and k columns, and obtaining an ith dynamic load amplitude S in the rain flow matrix a Column j dynamic load mean S m The corresponding number of cycles n ij (s a ,s m ) And according to the statistics of the rain flow count, the value of i is 1-h, and the value of j is 1-k.
Step S512: for shaft materials, an S-N curve is usually obtained by adopting a symmetrical cycle fatigue stress test with a stress average value of 0, the damage of the material under a specific load and corresponding cycle times is measured through the S-N curve, and fatigue life conversion is carried out according to a Goodman formula to obtain the following dynamic load amplitude S a And dynamic load mean S m The described equal-life curved surface C of the output shaft is shown in a formula (1):
in the formula (1), S a For dynamic load amplitude, S m For dynamic load mean, σ c The breaking strength of the shaft material is determined by the characteristics of the shaft material, m and c are constants, and N is the number of cycles.
Step S513: converting the formula (1) to obtain a dynamic load amplitude S a And dynamic load mean S m Corresponding maximum number of cycles N ij (s a ,s m ) And (5) performing fatigue test on the shaft material until fracture statistics.
Step S514: calculating to obtain the damage rate D of the output shaft shaft As shown in formula (2):
further, in step S5, the damage rate of the output gear is calculated, which specifically includes the following steps
For gear parts, the S-N curve of the gear material is shown as a formula (3):
N'S b ＝C 1 (3)
wherein N' is the cycle of stress circulation of the fatigue danger point of the gear, and each rotation of the gear is regarded as one cycle; s is the stress load amplitude of the fatigue danger point of the gear, the general linear relation between the stress load amplitude and the loading torque T is S=KT (K is a constant), and T is the loading torque applied by a fatigue fracture test and is determined by the material characteristics of gears; b and C 1 Is a gear material parameter.
Calculating the damage rate D of the fatigue dangerous part of the output gear under the random load g As shown in formula (4):
wherein n is p To correspond to loading torque T p Is actually rotated for a period of time, N p For loading torque T in S-N curve p Is a maximum number of revolutions.
Specifically, since K and C are in formula (4) 1 Are all the parameter constants of the gear materials,representing the damage degree to the fatigue dangerous part, which is called gear damage number, namely, the formula (4) is simplified to be shown in the formula (5):
in the above, the damage rate is adopted for the damage of the shaft parts, and the damage number is adopted for the damage of the gear parts, which are respectively used for measuring the damage degree corresponding to a section of dynamic load process. In the formula (5), the dynamic loading torque transmitted by the output gear along the axial direction is divided into q equal parts from the minimum value to the maximum value, and generally 8 equal parts are adopted, namely the q value is 8, and the dynamic loading torque can be adjusted according to actual needs.
Further, the dynamic loading torque T in step S6 load The dynamic torque average value, the dynamic torque amplitude and the loading frequency in the formula (6) can be adopted and can be determined according to the actual loading characteristic of the test bed. Wherein the dynamic torque average T m A specific gear can be adopted, namely, a dynamic load average value corresponding to a set gear in a set rotating speed interval is adopted, and a dynamic torque amplitude T a Can be determined as T m T is equivalent loading time, ω is loading frequency, specifically:
T load ＝T m +T a sin(ω·t) (6)
in the above description, the equivalent loading time t is mainly determined by the number of damages of the output gear as a constraint condition, and the larger the dynamic torque average value is, the shorter the equivalent loading time is. In the same equivalent loading time, the damage rate of the output shaft can be changed by changing the dynamic torque amplitude and the loading frequency, and the larger the dynamic torque amplitude is, the higher the loading frequency is, and the larger the damage rate of the output shaft is.
In the step, proper dynamic loading torque and equivalent loading time are selected according to the performance of the rack loading equipment, and the complete machine test of the comprehensive transmission device can be ensured, so that the damage rates of the output gear and the output shaft are achieved simultaneously, namely, the damage rates and the damage numbers corresponding to the output shaft and the output gear can be met simultaneously by adjusting the dynamic loading torque and the equivalent loading time.
The invention provides a method for testing the equivalent of a real-vehicle dynamic load stand of a transmission device, which is further described by a specific example and comprises the following steps:
the method comprises the steps of dividing the real vehicle dynamic load of the transmission device according to the forward gears 1, 2, 3, 4, 5, 6, reverse 1, reverse 2 and central steering gears, and dividing the transmission input rotation speed of the transmission device into 5 rotation speed intervals of 800-1200r/min,1200-1600r/min,1600-2000r/min,2000-2200r/min and 2200-2600r/min respectively.
For the dynamic load of the 1 st gear real vehicle with the rotating speed interval of 800-1200r/min, the damage rate D of the output shaft of the transmission device shown in the table 1 can be calculated shaft And the damage number D of the output gear gear For constraint conditions, different loading schemes are formulated to adapt to different bench test equipment, wherein two dynamic loading schemes are formulated as shown in scheme a and scheme b.
Table 11 injury calculation results
Scheme a: according to the dynamic torque average value 2745Nm, the dynamic torque amplitude is changed to +/-280 Nm, the loading frequency is 3.5Hz, the three are subjected to a loading test under the condition that the torque with a synthetic amplitude is taken as working condition, and the equivalent loading time is calculated to be 39min, so that the dynamic torque amplitude is increased, the damage rate of an output shaft is increased, the equivalent loading time of gear damage can ensure that the damage of an output gear and the damage of the output shaft can be achieved simultaneously, and specific test loading data and implementation schemes are shown in the table 2.
Table 2 1 step amplitude bench loading test protocol a
Scheme b: according to the dynamic torque average value 2534Nm, the dynamic torque amplitude is changed to +/-30 Nm, the loading frequency is 5.3Hz, the loading test is carried out under the condition that the torque with the synthesized amplitude is the working condition, the equivalent loading time of the load is calculated to be 59min, and the equivalent loading time of gear damage can also ensure that the damage of the output gear and the damage of the output shaft are achieved simultaneously. Specific test loading data and embodiments are shown in table 3.
Table 3 1 step amplitude bench loading test protocol b
The two loading schemes illustrate that the dynamic torque amplitude, the dynamic torque average value and the loading frequency are changed, and the corresponding equivalent loading time can be obtained under the constraint condition of equivalent damage of the output gear and the output shaft, so that the loading time of the bench can be shortened through the comparison scheme, and the purpose of accelerating the test is achieved. All loading motors on the market at present have the limitation of the response speed of the loading frequency, so the loading time of the loading motor under the physical constraint condition can be obtained by flexibly changing the combination of the dynamic torque amplitude and the dynamic torque average value.
Referring to fig. 3, the invention further provides an equivalent test system for a real vehicle dynamic load stand of a transmission device, which comprises:
torque test module: the torque testing device is used for carrying out real vehicle torque testing on the transmission device carrying vehicle to obtain a torque testing signal.
And a pretreatment module: the method is used for preprocessing the torque test signal to obtain the dynamic load and the transmission input rotating speed of the real vehicle.
The gear dividing module is used for: the dynamic load process corresponding to each gear is obtained by dividing according to the dynamic load of the real vehicle and the gears;
the interval dividing module: the transmission input rotating speed is divided into intervals according to the dynamic load process corresponding to each gear to obtain a rotating speed interval;
the damage calculation module: the damage rate is calculated according to the dynamic load process and the rotating speed interval and the output gear and the output shaft of the transmission device;
and an equivalent test module: and the method is used for determining the dynamic loading torque and the equivalent loading time of the set gear in the set rotating speed range by taking the obtained damage rate as a constraint condition, and carrying out a bench equivalent test.
Further, the damage calculation module comprises a shaft damage calculation module and a gear damage calculation module.
Specifically, the system provided in the embodiment of the present invention is specifically configured to execute the above method embodiment, and this is not repeated in the embodiment of the present invention.
The equivalent test method and the equivalent test system for the real-vehicle dynamic load rack of the transmission device can effectively check the durability of the output gear and the output shaft in the complete machine test, namely, the damage rate of the output shaft and the damage number of the output gear are taken as constraint conditions, the proper dynamic load torque characteristic and the equivalent load time can be selected according to the performance of the rack load equipment, the damage rate of the output gear and the output shaft in the complete machine test is ensured to be achieved simultaneously, the equivalent purpose of the real-vehicle dynamic load in the rack load damage is achieved, the pertinence and the comprehensiveness in the complete machine check test are improved, and the scientificity of the loading equivalent of the rack dynamic load is effectively improved.
The above examples are preferred embodiments of the present invention, but the embodiments of the present invention are not limited to the above examples, and any other changes, modifications, substitutions, combinations, and simplifications that do not depart from the spirit and principle of the present invention should be made in the equivalent manner, and the embodiments are included in the protection scope of the present invention.
Claims (3)
1. A real-vehicle dynamic load stand equivalent test method for a transmission device is characterized by comprising the following steps of: the method comprises the following steps:
carrying out real vehicle torque test on a transmission device carrying vehicle to obtain a torque test signal;
preprocessing a torque test signal to obtain a real vehicle dynamic load and a transmission input rotating speed;
dividing according to the actual vehicle dynamic load according to gears to obtain dynamic load courses corresponding to each gear;
dividing the transmission input rotating speed into sections according to the dynamic load process corresponding to each gear to obtain a rotating speed section;
calculating damage rates of an output gear and an output shaft of the transmission device according to the dynamic load process and the rotating speed interval;
determining dynamic loading torque and equivalent loading time of a set gear in a set rotating speed interval by taking the obtained damage rate as a constraint condition, and carrying out a bench equivalent test;
calculating the damage rate of the output shaft, specifically comprising:
the average value and the amplitude of the dynamic load of the real vehicle are respectively and evenly divided into k and h intervals, a rain flow matrix of h rows and k columns is constructed, and the dynamic load amplitude S is obtained a And dynamic load mean S m The corresponding number of cycles n ij (s a ,s m )；
According to the S-N curve of the shaft part, fatigue life conversion is carried out, and an equal-life curved surface C of the output shaft is obtained as shown in a formula (1):
wherein S is a S is the ith dynamic load amplitude in the rain flow matrix m For the j-th column dynamics in the rain flow matrixLoad mean value sigma c The fracture strength of the shaft material is that N is the number of times of circulation, m and c are constants;
converting the formula (1) to obtain a dynamic load amplitude S a And dynamic load mean S m Corresponding maximum number of cycles N ij (s a ,s m ) I is 1 to h, j is 1 to k;
calculating to obtain the damage rate D of the output shaft shaft As shown in formula (2):
calculating the damage rate of the output gear, specifically comprising:
the damage rate D of fatigue dangerous parts of the output gear under the random load g As shown in formula (4):
wherein n is p For loading torque T corresponding to fatigue fracture test p Is actually rotated for a period of time, N p Corresponding to loading torque T in S-N curve of output gear p Maximum number of rotations of b and C 1 The gear material parameter is K, and K is a constant;
the formula (4) is simplified to be shown as a formula (5), wherein p takes a value of 1-q, and the loading torque transmitted by the output gear along the axial direction is divided into q equal parts from the minimum value to the maximum value:
the dynamic loading torque T load Formula (6) shows:
T load ＝T m +T a sin(ω·t) (6)
wherein T is m For the dynamic torque average value, adopting a setting gear to correspond to a setting rotating speed intervalIs a dynamic load average value of (1); t (T) a For the dynamic torque amplitude, the dynamic torque average value T is set m 10% -20% of (a); t is equivalent loading time and is determined by the damage number of the output gear; ω is the loading frequency.
2. A system based on the equivalent test method of the real vehicle dynamic load stand of the transmission device according to claim 1, which is characterized in that: the system comprises:
torque test module: the torque testing device is used for carrying out real vehicle torque testing on the transmission device carrying vehicle to obtain a torque testing signal;
and a pretreatment module: the torque testing device is used for preprocessing the torque testing signal to obtain the dynamic load and the transmission input rotating speed of the real vehicle;
the gear dividing module is used for: the dynamic load process corresponding to each gear is obtained by dividing according to the dynamic load of the real vehicle and the gears;
the interval dividing module: the transmission input rotating speed is divided into intervals according to the dynamic load process corresponding to each gear to obtain a rotating speed interval;
the damage calculation module: the damage rate is calculated according to the dynamic load process and the rotating speed interval and the output gear and the output shaft of the transmission device;
and an equivalent test module: and the method is used for determining the dynamic loading torque and the equivalent loading time of the set gear in the set rotating speed range by taking the obtained damage rate as a constraint condition, and carrying out a bench equivalent test.
3. The transmission real vehicle dynamic load stand equivalent test system according to claim 2, wherein: the damage calculation module comprises a shaft damage calculation module and a gear damage calculation module.
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