Tilting rotorcraft transmission test device and method

Abstract

The invention discloses a tilt rotorcraft transmission test device and method, and the device comprises a test platform, the test platform is provided with a turnover driving mechanism and a rotation driving mechanism, and the turnover driving mechanism and the rotation driving mechanism are connected through a synchronization mechanism. The rotation driving mechanism is used for synchronously driving the two tilting rotor simulation systems to rotate, the two tilting rotor simulation systems are respectively mounted on the two synchronously tilting bases, the turnover driving mechanism is in transmission connection with the two synchronously tilting bases, and the turnover driving mechanism is used for driving the two bases to synchronously tilt. The synchronizing mechanism is connected in series with the tilting rotor simulation system, the rotation driving mechanism and the turnover driving mechanism, so that the tilting rotor simulation system and the rotation driving mechanism synchronously rotate while the turnover driving mechanism drives the base to turn over. The method comprises steps S1 to S11. According to the invention, transmission tests and tests of various flight attitudes can be carried out, quantitative and qualitative evaluation of transmission performance under dynamic random working conditions can be realized, and the accuracy and rationality of rotor transmission tests and tests are effectively improved.

Description

Technical Field

[0001] The present invention relates to the field of rotor transmission testing, and in particular to a test device and method for a tiltrotor transmission. Background Art

[0002] Tilt-rotor aircraft are more efficient aircraft that can significantly reduce take-off and landing distances and increase cruising speeds compared to fixed-wing aircraft and helicopters. However, when a tilt-rotor aircraft changes its flight mode during flight, the rotor tilts at an angle, and its overall transmission performance requirements are higher. Therefore, the transmission system of the tilt-rotor aircraft needs to undergo complex design and testing to ensure that the transmission system can maintain the stability of the overall structure and transmission performance when the tilt-rotor aircraft switches between take-off and landing states and cruising states, and avoid problems such as severe vibration and uneven force in the transmission system. Existing rotor test equipment can only test the rotation of the helicopter's rotors, and cannot test the transmission of the tilt-rotor aircraft, let alone the transmission test of the rotor rotation and tilt linkage. Therefore, there is an urgent need to propose a test device and method for the transmission of a tilt-rotor aircraft. Summary of the Invention

[0003] In view of the above-mentioned deficiencies in the prior art, the present invention provides a test device and method for a tiltrotor transmission, which can simulate the working state of the transmission system of a tiltrotor in different flight states and environments and evaluate the transmission performance.

[0004] In order to achieve the above-mentioned object of the invention, the technical solution adopted by the present invention is: A test device for tiltrotor transmission is provided, which includes a test platform. A flip drive mechanism and a rotation drive mechanism are respectively provided on the test platform. The flip drive mechanism and the rotation drive mechanism are connected by a synchronization mechanism. The rotation drive mechanism is used to synchronously drive two tiltrotor simulation systems to rotate. The two tiltrotor simulation systems are respectively installed on two synchronously tilting bases. The flip drive mechanism is connected to the two synchronously tilting bases through transmission. The flip drive mechanism is used to drive the two bases to tilt synchronously. The synchronization mechanism is connected in series with the tiltrotor simulation system, the rotation drive mechanism and the flip drive mechanism, so that the flip drive mechanism drives the base to flip while the tiltrotor simulation system and the rotation drive mechanism rotate synchronously.

[0005] Furthermore, the rotation drive mechanism includes a T-type transmission box, two first drive motors are respectively provided on both sides of the T-type transmission box, a first speed torque sensor is provided between the two first drive motors and the T-type transmission box, and the two ends of the first speed torque sensor are respectively connected to the first input end, the second input end and the two first drive motors on both sides of the T-type transmission box through a coupling; the output end of the T-type transmission box is respectively connected to the load motors on the two bases through the rotor transmission mechanism.

[0006] Furthermore, a first bevel gear is provided in the T-type transmission box, and the first bevel gear is installed on the first input shaft. One end of the first input shaft serves as the first input end of the T-type transmission box, and a second bevel gear is provided on the other end. Two intermediate bevel gears are engaged on both sides of the second bevel gear, and a third bevel gear is engaged between the two intermediate bevel gears. The second bevel gear, the two intermediate bevel gears and the third bevel gear form a mouth shape, and the two intermediate bevel gears are symmetrically arranged on the first bevel gear through the L-axis in a circle-centered manner; the third bevel gear is installed on the second input shaft, and the second input shaft serves as the second input end of the T-type transmission box; the first bevel gear is engaged with the fourth bevel gear in the T-type transmission box, and the fourth bevel gear is installed on the output end of the T-type transmission box.

[0007] Furthermore, the rotor transmission mechanism includes a fifth bevel gear installed at the output end of the T-type transmission box, the fifth bevel gear is meshed with the sixth bevel gear on the first transmission shaft, the first transmission shaft is perpendicular to the output end of the T-type transmission box, and seventh bevel gears are provided at both ends of the first transmission shaft, and the seventh bevel gears at both ends are respectively provided on one end of the two second transmission shafts, the second transmission shaft is perpendicular to the first transmission shaft, and an eighth bevel gear is provided on the other end of the two second transmission shafts, the eighth bevel gears on the two second transmission shafts are respectively meshed with the ninth bevel gears provided at one end of the two third transmission shafts, and the other ends of the two third transmission shafts are respectively connected to the two tilt-rotor simulation systems through a synchronization mechanism; the first transmission shaft, the second transmission shaft and the third transmission shaft are installed on the test platform through a bearing seat.

[0008] Furthermore, the tiltrotor simulation system includes a load motor mounted on a base, an output end of the load motor is transmission-connected to a second speed and torque sensor, and the second speed and torque sensor is connected to a synchronization mechanism via a coupling; The synchronization mechanism includes a swing box, a tenth bevel gear and an eleventh bevel gear. The tenth bevel gear is connected to the second speed torque sensor through a coupling. The tenth bevel gear is engaged with the eleventh bevel gear provided at the other end of the third transmission shaft. The eleventh bevel gear and the tenth bevel gear are provided in the swing box. The third transmission shaft extends into the swing box and rotates coaxially with the third transmission shaft.

[0009] Furthermore, the flip drive mechanism includes a flip drive motor, a third speed torque sensor and a reduction gearbox which are sequentially connected to the flip drive motor, the output end of the reduction gearbox being connected to a fourth transmission shaft, the ends of the fourth transmission shaft being sequentially provided with a bevel gear A and a bevel gear B, a gap being provided between the bevel gear A and the bevel gear B to accommodate the bevel gear C and the bevel gear D distributed on both sides of the fourth transmission shaft, and the bevel gear C and the bevel gear D are both engaged with the bevel gear A; Bevel gear C and bevel gear D are respectively arranged at one end of the coaxial fifth transmission shaft on both sides, and the other end of the fifth transmission shaft on both sides is respectively provided with the first gear and the second gear, the first gear and the third gear are connected through the intermediate gear, the second gear is meshed with the fourth gear, the bevel gear B is meshed with the bevel gear E set in the middle of the sixth transmission shaft, and the sixth transmission shaft is coaxial with the two third transmission shafts, and the two ends of the sixth transmission shaft are connected to the hanging ears set on both sides of the swing box.

[0010] Furthermore, the base includes a base plate, and swing rods are respectively provided on both sides of the base plate. The swing rods on both sides are respectively distributed on both sides of the swing box, and the end of the swing rod on one side is provided on the extension section of the swing bearing support through a shaft sleeve, the extension section is a hollow structure, and the extension section is rotatably connected to the shaft sleeve, and the end of the swing rod on the other side is provided with a semicircular collar, the collar is coaxially arranged with the third gear and the fourth gear, and the collar and the third gear and the fourth gear are connected by a pin to rotate synchronously; The two side ears are rotatably connected to the swing bearing supports on both sides, and the ears are rotatably connected to the bearings on the swing bearing supports. The end of the sixth transmission shaft passes through the swing bearing support on one side and is fixedly connected to the ear on one side. The third gear and the fourth gear are respectively rotatably connected to the extension section of the swing bearing support on one side through bearings.

[0011] Furthermore, the fourth transmission shaft is installed on the test platform through two bearing seats, and a flip limit mechanism is provided on the fourth transmission shaft between the two bearing seats. The flip limit mechanism includes a limit turntable, and two spaced limit pins are provided on the side of the limit turntable, one of which is fixed, and the other limit pin is inserted into the limit pin hole opened on the limit turntable. There are at least two limit pin holes arranged in parallel, and a limit shaft is provided on the bearing seat to block the limit pin. The limit shaft and the limit pin cooperate to limit the tilting angle of the base, and the other limit pin is inserted into different limit pin holes to adjust the tilting angle range of the base.

[0012] A test method for the tiltrotor transmission test device is provided, comprising the following steps: S1: The first drive motor or the second drive motor starts and outputs the set torque and speed The first speed torque sensor collects the actual torque output by the first drive motor or the second drive motor under zero load conditions. and speed ; S2: The second speed and torque sensor collects the torque under zero load conditions and speed , calculate the transmission torque error and transmission speed error ; S3: Construct a wind speed power spectrum model under turbulent random fluctuations of wind load; ; in, f is the frequency, is the frequency fluctuation coefficient, the frequency coefficient Pick A random number between is the turbulence length, and for low-altitude flight, it is 50~100m. V is the target wind speed of the test (m / s), is the variance of the longitudinal wind speed based on the turbulence intensity, is the turbulent wind speed power of the test, T is the load cycle, N is the number of times the load is applied during the load cycle; S4: Set a fixed turbulent wind speed power and calculate the power of the wind speed power spectrum model during the load cycle. T At different times t Fluctuating wind speed values , and based on the fluctuating wind speed value Calculating the duty cycle T Load force at different times ; ; in, is the air density, c The rotor chord length of the test setup is, r is the rotor radius, is the drag generated by the rotor, U is the rotor rotation speed; S5: According to load force Calculate the load cycle of the rotor T Load torque at different times ; ; in, is the load cell length of the rotor; S6: Start the load motor to load the dynamic load, so that the torque data collected by the second speed torque sensor meets the load torque , and obtain real-time speed ; S7: The flip drive motor drives the swing box and the base to swing back and forth at a fixed rate; S8: The first speed torque sensor collects the load torque Real-time torque under conditions and real-time speed , and according to the transmission torque error and transmission speed error Calculate torque ripple under different load conditions and speed fluctuation value ; ; S9: According to the torque fluctuation value and speed fluctuation value , during the load cycle T Uniform internal m sampling points, and obtain the torque fluctuation value data corresponding to each sampling point and speed fluctuation data , For the m The torque fluctuation value corresponding to the sampling point is For the m The speed fluctuation value corresponding to the sampling point is t m For the m The time corresponding to each sampling point; S10: Set the allowable value of torque fluctuation and the allowable value of speed fluctuation , calculated in the test cycle T Transmission performance coefficient of the inner rotor transmission mechanism f ; ; in, k is the number of the sampling point, For the k The torque fluctuation value corresponding to the sampling point is For the k The speed fluctuation value corresponding to the sampling point is t k For the k The time corresponding to each sampling point is They are the weight coefficients of torque fluctuation and speed fluctuation on rotor transmission performance, generally taken as ; S11: Set the threshold of transmission performance coefficient ,like , the transmission performance of the rotor transmission mechanism meets the requirements, otherwise, it does not meet the requirements.

[0013] The beneficial effects of the present application are: the present application provides working load for the constructed measured rotor transmission mechanism by setting the load motor, simulates the real working environment, and the present application further realizes the simulation and test of the real working environment by outputting real-time random dynamic load of the load motor. The flip drive motor serves as the power source of the flip swing, realizes the synchronization of the flip and the rotor rotation through the series connection of the synchronous mechanism, can carry out the transmission test and experiment of various flight attitudes, and can realize the quantitative and qualitative evaluation of the transmission performance under the dynamic random working condition, effectively improves the accuracy and rationality of the measured rotor transmission test and experiment. BRIEF DESCRIPTION OF DRAWINGS

[0014] Figure 1 It is a perspective view of the test device for the transmission of the tilt rotor aircraft.

[0015] Figure 2 It is a structure diagram of the series connection of the tilt rotor simulation system and the flip driving mechanism.

[0016] Figure 3 It is a structure diagram of the flip limiting mechanism.

[0017] Figure 4 It is a connection structure diagram of the sixth transmission shaft and the swing box.

[0018] Among them, 1, the first drive motor, 2, the first rotation speed torque sensor, 3, the T-shaped transmission box, 4, the first bevel gear, 5, the intermediate bevel gear, 6, the fourth bevel gear, 7, the fifth bevel gear, 8, the first transmission shaft, 9, the seventh bevel gear, 10, the second transmission shaft, 11, the third transmission shaft, 12, the ninth bevel gear, 13, the swing box, 14, the second rotation speed torque sensor, 15, the load motor, 16, the reduction box, 17, the third rotation speed torque sensor, 18, the flip drive motor, 19, the fourth transmission shaft, 20, the fifth transmission shaft, 21, the sixth transmission shaft, 22, the base plate, 23, the swing rod, 24, the shaft sleeve, 25, the bevel gear B, 26, the bevel gear A, 27, the limiting turntable, 28, the sleeve ring, 29, the bearing seat, 30, the limiting pin shaft, 31, the third gear, 32, the limiting shaft, 33, the eleventh bevel gear, 34, the extension section, 35, the bolt, 36, the swing bearing support, 37, the lug. DETAILED DESCRIPTION

[0019] The specific embodiments of the present application are described below to facilitate the understanding of the present application by those skilled in the art, but it should be clear that the present application is not limited to the scope of the specific embodiments, and for those skilled in the art, it is obvious that various changes are within the spirit and scope of the present application defined and determined by the appended claims, and all the inventions utilizing the concept of the present application are within the scope of protection.

[0020] AsFigures 1-4 As shown, a test device for tiltrotor transmission includes a test platform, on which a flip drive mechanism and a rotation drive mechanism are respectively provided. The flip drive mechanism and the rotation drive mechanism are connected by a synchronization mechanism. The rotation drive mechanism is used to synchronously drive two tiltrotor simulation systems to rotate. The two tiltrotor simulation systems are respectively installed on two synchronously tilting bases. The flip drive mechanism is connected to the two synchronously tilting bases through transmission. The flip drive mechanism is used to drive the two bases to tilt synchronously. The synchronization mechanism is connected in series with the tiltrotor simulation system, the rotation drive mechanism and the flip drive mechanism, so that the flip drive mechanism drives the base to flip while the tiltrotor simulation system and the rotation drive mechanism rotate synchronously.

[0021] In this embodiment, the rotation drive mechanism includes a T-type transmission box 3, two first drive motors 1 are respectively provided on both sides of the T-type transmission box 3, a first speed torque sensor 2 is provided between the two first drive motors 1 and the T-type transmission box 3, and the two ends of the first speed torque sensor 2 are respectively connected to the first input end, the second input end and the two first drive motors 1 on both sides of the T-type transmission box 3 through a coupling; the output end of the T-type transmission box 3 is respectively connected to the load motors 15 on the two bases through the rotor transmission mechanism.

[0022] Both first drive motors 1 can be used as power devices for the rotor transmission mechanism, wherein one first drive motor 1 serves as the main drive motor and the other serves as a redundant drive motor. When the main drive motor fails, the transmission mechanism power remains normal.

[0023] In this embodiment, a first bevel gear 4 is provided in the T-type transmission case 3 and is mounted on the first input shaft. One end of the first input shaft serves as the first input end of the T-type transmission case 3, and a second bevel gear is provided on the other end. Two intermediate bevel gears 5 are meshed on either side of the second bevel gear, and a third bevel gear is meshed between the two intermediate bevel gears 5. The second bevel gear, the two intermediate bevel gears 5, and the third bevel gear form a mouth shape, and the two intermediate bevel gears 5 are symmetrically arranged on the first bevel gear 4 through the L axis. The third bevel gear is mounted on the second input shaft, which serves as the second input end of the T-type transmission case 3. The first bevel gear 4 meshes with the fourth bevel gear 6 in the T-type transmission case 3, and the fourth bevel gear 6 is mounted on the output end of the T-type transmission case 3. The design of the T-type transmission case 3 allows the two first drive motors 1 to output power simultaneously and achieve differential power output.

[0024] In this embodiment, the rotor transmission mechanism includes a fifth bevel gear 7 mounted at the output end of a T-type transmission case 3. The fifth bevel gear 7 meshes with a sixth bevel gear on a first transmission shaft 8. The first transmission shaft 8 is perpendicular to the output end of the T-type transmission case 3. Seventh bevel gears 9 are provided at each end of the first transmission shaft 8. The seventh bevel gears 9 are respectively mounted on one end of two second transmission shafts 10. The second transmission shafts 10 are perpendicular to the first transmission shaft 8. Eighth bevel gears are provided on the other ends of the two second transmission shafts 10. The eighth bevel gears on the two second transmission shafts 10 mesh with ninth bevel gears 12 mounted on one end of two third transmission shafts 11. The other ends of the two third transmission shafts 11 are connected to two tiltrotor simulation systems via synchronization mechanisms. The first, second, and third transmission shafts 8, 10, and 11 are mounted on the test platform via bearing blocks 29. The first, second, and third transmission shafts 10, 11, and their associated bevel gears form an equivalent rotor transmission mechanism, effectively simulating the transmission process of a real rotor transmission mechanism.

[0025] In this embodiment, the tiltrotor simulation system includes a load motor 15 mounted on a base. The output end of load motor 15 is in transmission connection with a second speed and torque sensor 14, which is connected to a synchronization mechanism via a coupling. Load motor 15 outputs the load borne by the rotor during flight, simulating the transmission process under loaded conditions.

[0026] The synchronization mechanism includes a swing box 13, a tenth bevel gear and an eleventh bevel gear 33. The tenth bevel gear is connected to the second speed torque sensor 14 through a coupling. The tenth bevel gear is engaged with the eleventh bevel gear 33 provided at the other end of the third transmission shaft 11. The eleventh bevel gear 33 and the tenth bevel gear are arranged in the swing box 13. The third transmission shaft 11 extends into the swing box 13 and rotates coaxially with the third transmission shaft 11.

[0027] In this embodiment, the flip drive mechanism includes a flip drive motor 18, a third speed torque sensor 17 and a reduction gear 16 that are sequentially connected to the flip drive motor 18. The output end of the reduction gear 16 is connected to a fourth transmission shaft 19. The ends of the fourth transmission shaft 19 are sequentially provided with a bevel gear A26 and a bevel gear B25. A gap is provided between the bevel gear A26 and the bevel gear B25 to accommodate the bevel gear C and the bevel gear D distributed on both sides of the fourth transmission shaft 19. The bevel gear C and the bevel gear D are both engaged with the bevel gear A26. Bevel gear C and bevel gear D are respectively arranged at one end of the coaxial fifth transmission shaft 20 on both sides, and the other ends of the fifth transmission shaft 20 on both sides are respectively provided with the first gear and the second gear. The first gear is connected to the third gear 31 through an intermediate gear transmission, and the second gear is meshed with the fourth gear; the bevel gear B25 is meshed with the bevel gear E set in the middle of the sixth transmission shaft 21, and the sixth transmission shaft 21 is coaxial with the two third transmission shafts 11, and the two ends of the sixth transmission shaft 21 are connected to the hanging ears 37 set on both sides of the swing box 13.

[0028] In this embodiment, the base includes a base plate 22, and swing rods 23 are respectively provided on both sides of the base plate 22. The swing rods 23 on both sides are respectively distributed on both sides of the swing box 13, and the end of the swing rod 23 on one side is set on the extension section 34 of the swing bearing support 36 through the shaft sleeve 24. The extension section 34 is a hollow structure, and the extension section 34 is rotatably connected to the shaft sleeve 24. A semicircular ring 28 is provided at the end of the swing rod 23 on the other side. The ring 28 is coaxially arranged with the third gear 31 and the fourth gear. The ring 28 is connected with the third gear 31 and the fourth gear through a pin 35 and rotates synchronously.

[0029] The two side ears 37 are rotatably connected to the swing bearing supports 36 on both sides, and the ears 37 are rotatably connected to the bearings on the swing bearing supports 36. The end of the sixth transmission shaft 21 passes through one side of the swing bearing supports 36 and is fixedly connected to one side of the ears 37. The third gear 31 and the fourth gear are respectively rotatably connected to the extension section 34 of one side of the swing bearing supports 36 through bearings.

[0030] Bevel gears C and D are both meshed with bevel gear A26, causing the fifth transmission shafts 20 on both sides to rotate in opposite directions. Therefore, an intermediate gear is provided between the first gear and the third gear 31 to change the direction of the third gear 31, ensuring that the third gear 31 and the fourth gear rotate in the same direction. At the same time, the lugs of the swing box 13 are rotatably connected to the swing bearing support 36, playing a supporting role. This ensures that the load motor 15 and the swing box 13 remain synchronized during the tilting process, and the flip drive motor 18 provides stable power for the swing box 13 and the base plate 22 when they tilt. The function of the intermediate gear is to change the rotation direction of the driven gear so that the left and right base plates 22 are lifted and rotated in the same direction and at the same speed.

[0031] In this embodiment, the fourth transmission shaft 19 is installed on the test platform through two bearing seats 29. A flip limit mechanism is provided on the fourth transmission shaft 19 between the two bearing seats 29. The flip limit mechanism includes a limit turntable 27. Two spaced limit pins 30 are provided on the side of the limit turntable 27. One of the limit pins 30 is fixed, and the other limit pin 30 is inserted into the limit pin hole opened on the limit turntable 27. There are at least two limit pin holes arranged in parallel. A limit shaft 32 is provided on the bearing seat 29 to block the limit pin 30. The limit shaft 32 cooperates with the limit pin 30 to limit the tilting angle of the base. The other limit pin 30 is inserted into different limit pin holes to adjust the tilting angle range of the base.

[0032] A test method for the tiltrotor transmission test device is provided, comprising the following steps: S1: The first drive motor 1 or the second drive motor starts and outputs the set torque and speed The first speed torque sensor 2 collects the actual torque output by the first drive motor 1 or the second drive motor under zero load conditions. and speed ; S2: The second speed and torque sensor 14 collects the torque under zero load conditions and speed , calculate the transmission torque error and transmission speed error ; S3: Construct a wind speed power spectrum model under turbulent random fluctuations of wind load; ; in, f is the frequency, is the frequency fluctuation coefficient, the frequency coefficient Pick A random number between is the turbulence length, and for low-altitude flight, it is 50~100m. V is the target wind speed of the test (m / s), is the variance of the longitudinal wind speed based on the turbulence intensity, is the turbulent wind speed power of the test, T is the load cycle, N It is the number of times the load is applied within the load cycle. When loading the power of the wind load, the present invention introduces a sine function to randomize the frequency and calculates the wind load at the random frequency to achieve the purpose of simulating the random wind load.

[0033] S4: Set a fixed turbulent wind speed power and calculate the power of the wind speed power spectrum model during the load cycle. T At different timest Fluctuating wind speed values , and based on the fluctuating wind speed value Calculating the duty cycle T Load force at different times ; ; in, is the air density, c The rotor chord length of the test setup is, r is the rotor radius, is the drag generated by the rotor, U is the rotor rotation speed; S5: According to load force Calculate the load cycle of the rotor T Load torque at different times ; ; in, is the load cell length of the rotor; S6: Start the load motor 15 to load the dynamic load, so that the torque data collected by the second speed torque sensor 14 meets the load torque , and obtain real-time speed ; S7: The flip drive motor 18 drives the swing box 13 and the base to swing back and forth at a fixed speed; S8: The first speed torque sensor 2 collects the load torque Real-time torque under conditions and real-time speed , and according to the transmission torque error and transmission speed error Calculate torque ripple under different load conditions and speed fluctuation value ; ; S9: According to the torque fluctuation value and speed fluctuation value , during the load cycle T Uniform internal m sampling points, and obtain the torque fluctuation value data corresponding to each sampling point and speed fluctuation data , For the m The torque fluctuation value corresponding to the sampling point is For the m The speed fluctuation value corresponding to the sampling point is t m For the mThe time corresponding to each sampling point; S10: Set the allowable value of torque fluctuation and the allowable value of speed fluctuation , calculated in the test cycle T Transmission performance coefficient of the inner rotor transmission mechanism f ; ; in, k is the number of the sampling point, For the k The torque fluctuation value corresponding to the sampling point is For the k The speed fluctuation value corresponding to the sampling point is t k For the k The time corresponding to each sampling point is They are the weight coefficients of torque fluctuation and speed fluctuation on rotor transmission performance, generally taken as ; S11: Set the threshold of the transmission performance coefficient ,like , the transmission performance of the rotor transmission mechanism meets the requirements, otherwise, it does not meet the requirements.

[0034] The present invention simulates a real-world operating environment by providing a load motor 15 to provide a workload for the constructed rotor transmission mechanism under test. Furthermore, the present invention further achieves simulation and testing of a real-world operating environment by outputting a real-time, random dynamic load through load motor 15. The flip drive motor 18, serving as the power source for flipping and swinging, synchronizes flipping with rotor rotation through a series connection with a synchronization mechanism. This allows transmission testing and experimentation in various flight attitudes, and quantitative and qualitative evaluation of transmission performance under dynamic, random conditions, effectively improving the accuracy and rationality of rotor transmission testing and experimentation.

Claims

1. A test device for tiltrotor transmission, characterized in that: The invention comprises a test platform, on which a flipping drive mechanism and a rotation drive mechanism are respectively provided. The flipping drive mechanism and the rotation drive mechanism are connected by a synchronization mechanism. The rotation drive mechanism is used to synchronously drive two tilt-rotor simulation systems to rotate. The two tilt-rotor simulation systems are respectively installed on two synchronously tilting bases. The flipping drive mechanism is connected to the two synchronously tilting bases by transmission. The flipping drive mechanism is used to drive the two bases to tilt synchronously. The synchronization mechanism is connected in series with the tilt-rotor simulation system, the rotation drive mechanism and the flipping drive mechanism, so that the flipping drive mechanism drives the base to flip while the tilt-rotor simulation system and the rotation drive mechanism rotate synchronously.

2. The tiltrotor transmission test device according to claim 1, characterized in that: The rotation drive mechanism includes a T-type transmission box, two first drive motors are respectively provided on both sides of the T-type transmission box, a first speed torque sensor is provided between the two first drive motors and the T-type transmission box, and the two ends of the first speed torque sensor are respectively connected to the first input end, the second input end and the two first drive motors on both sides of the T-type transmission box through a coupling; the output end of the T-type transmission box is respectively connected to the load motors on the two bases through the rotor transmission mechanism.

3. The tiltrotor transmission test device according to claim 2, characterized in that: A first bevel gear is provided in the T-type transmission box, and the first bevel gear is mounted on the first input shaft. One end of the first input shaft serves as the first input end of the T-type transmission box, and a second bevel gear is provided on the other end. Two intermediate bevel gears are engaged on both sides of the second bevel gear, and a third bevel gear is engaged between the two intermediate bevel gears. The second bevel gear, the two intermediate bevel gears and the third bevel gear form a mouth shape, and the two intermediate bevel gears are symmetrically arranged on the first bevel gear through the L-axis in a circle-centered manner; the third bevel gear is mounted on the second input shaft, and the second input shaft serves as the second input end of the T-type transmission box; the first bevel gear is engaged with the fourth bevel gear in the T-type transmission box, and the fourth bevel gear is mounted on the output end of the T-type transmission box.

4. The tiltrotor transmission test device according to claim 3, characterized in that: The rotor transmission mechanism includes a fifth bevel gear installed at the output end of the T-type transmission box, the fifth bevel gear is meshed with the sixth bevel gear on the first transmission shaft, the first transmission shaft is perpendicular to the output end of the T-type transmission box, and seventh bevel gears are provided at both ends of the first transmission shaft. The seventh bevel gears at both ends are respectively provided on one end of the two second transmission shafts, the second transmission shaft is perpendicular to the first transmission shaft, and an eighth bevel gear is provided on the other end of the two second transmission shafts. The eighth bevel gears on the two second transmission shafts are respectively meshed with the ninth bevel gears provided on one end of the two third transmission shafts, and the other ends of the two third transmission shafts are respectively connected to the two tilt-rotor simulation systems through a synchronization mechanism; the first transmission shaft, the second transmission shaft and the third transmission shaft are installed on the test platform through a bearing seat.

5. The tiltrotor transmission test device according to claim 4, characterized in that: The tiltrotor simulation system includes a load motor mounted on a base, wherein an output end of the load motor is transmission-connected to a second speed and torque sensor, and the second speed and torque sensor is connected to a synchronization mechanism via a coupling; The synchronization mechanism includes a swing box, a tenth bevel gear and an eleventh bevel gear. The tenth bevel gear is connected to the second speed torque sensor through a coupling. The tenth bevel gear is engaged with the eleventh bevel gear provided at the other end of the third transmission shaft. The eleventh bevel gear and the tenth bevel gear are provided in the swing box. The third transmission shaft extends into the swing box and rotates coaxially with the third transmission shaft.

6. The tiltrotor transmission test device according to claim 5, characterized in that: The flip drive mechanism includes a flip drive motor, a third speed torque sensor and a reduction gear box which are sequentially connected to the flip drive motor, the output end of the reduction gear box is connected to a fourth transmission shaft, the ends of the fourth transmission shaft are sequentially provided with a bevel gear A and a bevel gear B, a gap is provided between the bevel gear A and the bevel gear B to accommodate the bevel gear C and the bevel gear D distributed on both sides of the fourth transmission shaft, and the bevel gear C and the bevel gear D are both engaged with the bevel gear A; The bevel gear C and the bevel gear D are respectively arranged at one end of the coaxial fifth transmission shaft on both sides, and the other end of the fifth transmission shaft on both sides is respectively provided with a first gear and a second gear, the first gear and the third gear are connected through an intermediate gear, and the second gear is meshed with the fourth gear, the bevel gear B is meshed with the bevel gear E arranged in the middle of the sixth transmission shaft, and the sixth transmission shaft is coaxial with the two third transmission shafts, and the two ends of the sixth transmission shaft are connected to the hanging ears arranged on both sides of the swing box.

7. The tiltrotor transmission test device according to claim 6, characterized in that: The base includes a base plate, and swing rods are respectively provided on both sides of the base plate. The swing rods on both sides are respectively distributed on both sides of the swing box, and the end of the swing rod on one side is set on the extension section of the swing bearing support through a shaft sleeve. The extension section is a hollow structure and is rotatably connected to the shaft sleeve. The end of the swing rod on the other side is provided with a semicircular collar, and the collar is coaxially arranged with the third gear and the fourth gear. The collar and the third gear and the fourth gear are connected by a pin and rotate synchronously. The lugs on both sides are rotatably connected to the swing bearing supports on both sides, and the lugs are rotatably connected to the bearings on the swing bearing supports. The end of the sixth transmission shaft passes through the swing bearing support on one side and is fixedly connected to the lug on one side. The third gear and the fourth gear are respectively rotatably connected to the extended section of the swing bearing support on one side through bearings.

8. The tiltrotor transmission test device according to claim 7, characterized in that: The fourth transmission shaft is installed on the test platform through two bearing seats. A flip limit mechanism is provided on the fourth transmission shaft between the two bearing seats. The flip limit mechanism includes a limit turntable. Two spaced limit pins are provided on the side of the limit turntable, one of the limit pins is fixed, and the other limit pin is inserted into the limit pin hole opened on the limit turntable. There are at least two limit pin holes arranged in parallel. A limit shaft for blocking the limit pin is provided on the bearing seat. The limit shaft cooperates with the limit pin to limit the tilting angle of the base. The other limit pin is inserted into different limit pin holes to adjust the tilting angle range of the base.

9. A test method for the tiltrotor transmission test device according to claim 8, characterized in that: The following steps are involved: S1: The first drive motor or the second drive motor starts and outputs the set torque and speed The first speed torque sensor collects the actual torque output by the first drive motor or the second drive motor under zero load conditions. and speed ; S2: The second speed and torque sensor collects the torque under zero load conditions and speed , calculate the transmission torque error and transmission speed error ; S3: Construct a wind speed power spectrum model under turbulent random fluctuations of wind load; ； in, f is the frequency, is the frequency fluctuation coefficient, the frequency coefficient Pick A random number between is the turbulence length, V is the target wind speed of the test, is the variance of the longitudinal wind speed based on the turbulence intensity, is the turbulent wind speed power of the test, T is the load cycle, N is the number of times the load is applied during the load cycle; S4: Set a fixed turbulent wind speed power and calculate the power of the wind speed power spectrum model during the load cycle. T At different times t Fluctuating wind speed values , and based on the fluctuating wind speed value Calculating the duty cycle T Load force at different times ; ； in, is the air density, c The rotor chord length of the test setup is, r is the rotor radius, is the drag generated by the rotor, U is the rotor rotation speed; S5: According to load force Calculate the load cycle of the rotor T Load torque at different times ; ； in, is the load cell length of the rotor; S6: Start the load motor to load the dynamic load, so that the torque data collected by the second speed torque sensor meets the load torque , and obtain real-time speed ; S7: The flip drive motor drives the swing box and the base to swing back and forth at a fixed rate; S8: The first speed torque sensor collects the load torque Real-time torque under conditions and real-time speed , and according to the transmission torque error and transmission speed error Calculate torque ripple under different load conditions and speed fluctuation value ; ； S9: According to the torque fluctuation value and speed fluctuation value , during the load cycle T Uniform internal m sampling points, and obtain the torque fluctuation value data corresponding to each sampling point and speed fluctuation data , For the m The torque fluctuation value corresponding to the sampling point is For the m The speed fluctuation value corresponding to the sampling point is t m For the m The time corresponding to each sampling point; S10: Set the allowable value of torque fluctuation and the allowable value of speed fluctuation , calculated in the test cycle T Transmission performance coefficient of the inner rotor transmission mechanism f ; ； in, k is the number of the sampling point, For the k The torque fluctuation value corresponding to the sampling point is For the k The speed fluctuation value corresponding to the sampling point is t k For the k The time corresponding to each sampling point is are the weight coefficients of the effects of torque fluctuation and speed fluctuation on rotor transmission performance; S11: Set the threshold of transmission performance coefficient ,like , the transmission performance of the rotor transmission mechanism meets the requirements, otherwise, it does not meet the requirements.

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