A test apparatus and method for the transmission of a tiltrotor aircraft.

Abstract

This invention discloses a test apparatus and method for tiltrotor aircraft transmission. The apparatus includes a test platform, on which a tilting drive mechanism and a rotation drive mechanism are respectively arranged. The tilting 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 mounted on two synchronously tilting bases. The tilting drive mechanism is transmissionally connected to the two synchronously tilting bases and is used to drive the two bases to tilt synchronously. The synchronization mechanism connects the tiltrotor simulation system, the rotation drive mechanism, and the tilting drive mechanism in series, so that while the tilting drive mechanism drives the bases to tilt, the tiltrotor simulation system and the rotation drive mechanism rotate synchronously. The method includes steps S1-S11. This invention can perform transmission tests and experiments in various flight attitudes and can realize quantitative and qualitative evaluation of transmission performance under dynamic random conditions, effectively improving the accuracy and rationality of tiltrotor transmission tests and experiments.

Description

Technical Field

[0001] This invention relates to the field of rotor drive testing, and more specifically to a test apparatus and method for tiltrotor aircraft transmission. Background Technology

[0002] Tiltrotors, as more efficient aircraft, can significantly reduce takeoff and landing distances and increase cruise speeds compared to fixed-wing aircraft and helicopters. However, when changing flight modes during flight, the rotor tilts, requiring higher overall transmission performance. Therefore, the transmission system of a tiltrotor needs complex design and testing to ensure the stability and transmission performance of the overall structure during the transition between takeoff / landing and cruise states, avoiding problems such as severe vibration and uneven stress. Existing rotor testing equipment can only test the rotor rotation of helicopters, not the transmission of tiltrotors, let alone the transmission that links rotor rotation and tilt. Therefore, there is an urgent need to propose a testing device and method for the transmission of tiltrotors. Summary of the Invention

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

[0004] To achieve the above-mentioned objectives, the technical solution adopted by this invention is as follows:

[0005] A test apparatus for tiltrotor transmission is provided, comprising a test platform on which a tilting drive mechanism and a rotation drive mechanism are respectively arranged. The tilting 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 mounted on two synchronously tilting bases. The tilting drive mechanism is driven by the two synchronously tilting bases and is used to drive the two bases to tilt synchronously. The synchronization mechanism connects the tiltrotor simulation system, the rotation drive mechanism, and the tilting drive mechanism in series, so that while the tilting drive mechanism drives the bases to tilt, the tiltrotor simulation system and the rotation drive mechanism rotate synchronously.

[0006] Furthermore, the rotation drive mechanism includes a T-shaped transmission box, with two first drive motors respectively arranged on both sides of the T-shaped transmission box. A first speed and torque sensor is arranged between the two first drive motors and the T-shaped transmission box, and the two ends of the first speed and 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-shaped transmission box through couplings. The output end of the T-shaped transmission box is respectively connected to the load motors on the two bases through a rotor transmission mechanism.

[0007] Furthermore, a first bevel gear is installed inside the T-shaped transmission box. 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-shaped transmission box, and a second bevel gear is installed on the other end. Two intermediate bevel gears mesh on both sides of the second bevel gear, and a third bevel gear meshes between the two intermediate bevel gears. The second bevel gear, the two intermediate bevel gears, and the third bevel gear form an opening shape, and the two intermediate bevel gears are symmetrically arranged on the first bevel gear at the center through an L-shaped shaft. The third bevel gear is mounted on the second input shaft, which serves as the second input end of the T-shaped transmission box. The first bevel gear meshes with a fourth bevel gear inside the T-shaped transmission box, and the fourth bevel gear is mounted on the output end of the T-shaped transmission box.

[0008] Furthermore, the rotor transmission mechanism includes a fifth bevel gear mounted on the output end of the T-shaped transmission box. The fifth bevel gear meshes with a sixth bevel gear on the first transmission shaft. The first transmission shaft is perpendicular to the output end of the T-shaped transmission box. Seventh bevel gears are provided at both ends of the first transmission shaft. The seventh bevel gears at both ends are respectively located on one end of two second transmission shafts. The second transmission shafts are perpendicular to the first transmission shaft. An eighth bevel gear is provided on the other end of each of the two second transmission shafts. The eighth bevel gears on the two second transmission shafts mesh with ninth bevel gears located on one end of two third transmission shafts. The other ends of the two third transmission shafts are respectively connected to two tilting rotor simulation systems through a synchronization mechanism. The first, second, and third transmission shafts are mounted on the test platform through bearing seats.

[0009] Furthermore, the tilt rotor simulation system includes a load motor mounted on a base, the output of which is connected to a second speed and torque sensor, which is connected to a synchronization mechanism via a coupling.

[0010] 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 and torque sensor via a coupling. The tenth bevel gear meshes with the eleventh bevel gear located at the other end of the third drive shaft. The eleventh bevel gear and the tenth bevel gear are located inside the swing box. The third drive shaft extends into the swing box and rotates coaxially with the swing box.

[0011] Furthermore, the tilting drive mechanism includes a tilting drive motor, a third speed and torque sensor and a reduction gearbox that are sequentially connected to the tilting drive motor, and a fourth drive shaft connected to the output end of the reduction gearbox. A bevel gear A and a bevel gear B are sequentially provided at the end of the fourth drive shaft. 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 drive shaft. Both the bevel gear C and the bevel gear D mesh with the bevel gear A.

[0012] Bevel gear C and bevel gear D are respectively set at one end of the fifth transmission shaft on both sides. The other end of the fifth transmission shaft on both sides is respectively set with a first gear and a second gear. The first gear and the third gear are connected by a transmission through an intermediate gear. The second gear and the fourth gear mesh. Bevel gear B meshes with bevel gear E set in the middle of the sixth transmission shaft. The sixth transmission shaft is coaxial with the two third transmission shafts. The two ends of the sixth transmission shaft are connected to the lugs set on both sides of the swing box.

[0013] Furthermore, the base includes a base plate, and swing rods are respectively provided on both sides of the base plate. The swing rods are distributed on both sides of the swing box, and the end of one swing rod is provided on the extension section of the swing bearing support through a bushing. The extension section is a hollow structure and is rotatably connected to the bushing. The end of the other swing rod is provided with a semi-circular collar. The collar is coaxially arranged with the third gear and the fourth gear. The collar is connected to the third gear and the fourth gear through a pin and rotates synchronously.

[0014] The two side lugs are rotatably connected to the two side swing bearing supports, and the lugs are rotatably connected to the bearings on the swing bearing supports. The end of the sixth drive shaft passes through one side of the swing bearing support and is fixedly connected to one side of the lug. The third gear and the fourth gear are rotatably connected to the extension section of one side of the swing bearing support through bearings.

[0015] Furthermore, the fourth drive shaft is mounted on the test platform via two bearing seats. A tilting and limiting mechanism is provided on the fourth drive shaft between the two bearing seats. The tilting and limiting mechanism includes a limiting turntable. Two spaced limiting pins are provided on the side of the limiting turntable. One limiting pin is fixed, and the other limiting pin is inserted into a limiting pin hole opened on the limiting turntable. At least two limiting pins are arranged side by side in the limiting pin hole. A limiting shaft is provided on the bearing seat to block the limiting pin. The limiting shaft and the limiting pin cooperate to limit the tilt angle of the base. The other limiting pin is inserted into different limiting pin holes to adjust the tilt angle range of the base.

[0016] A test method for the above-mentioned tiltrotor engine transmission test device is provided, comprising the following steps:

[0017] S1: The first or second drive motor starts and outputs the set torque. and rotational speed The first speed and torque sensor collects the actual torque output by the first or second drive motor under zero-load conditions. and rotational speed ;

[0018] S2: The second speed and torque sensor collects torque under zero-load conditions. and rotational speed Calculate the transmission torque error and transmission speed error ;

[0019] S3: Constructing a wind speed power spectrum model under wind load turbulent random fluctuations;

[0020] ;

[0021] in, f For frequency, For frequency fluctuation coefficient, frequency coefficient Pick Random numbers between The turbulence length is taken as 50-100m for low-altitude flight. V The target wind speed (m / s) for the experiment. The variance of longitudinal wind speed based on turbulence intensity. The power of the turbulent wind speed in the experiment, T For the load cycle, N The number of times the load is applied within a load cycle;

[0022] S4: Set a fixed turbulent wind speed power, and calculate the power during the load cycle based on the wind speed power spectrum model. T Different times within t fluctuating wind speed value And based on fluctuating wind speed values Calculate load cycle T Load force at different times ;

[0023] ;

[0024] in, air density, c The rotor chord length set for the experiment, r The rotor radius is... The drag generated by the rotor, U This refers to the rotor rotation speed;

[0025] S5: Based on load capacity Calculate the rotor during the load cycle T Load torque at different times ;

[0026] ;

[0027] in, The length of the rotor's load unit;

[0028] S6: Start the load motor to apply the dynamic load, ensuring that the torque data collected by the second speed and torque sensor meets the load torque requirements. And obtain the real-time rotation speed. ;

[0029] S7: The flip drive motor drives the swing box and base to reciprocate at a fixed rate;

[0030] S8: The first speed and torque sensor collects data on the load torque. Real-time torque under certain conditions and real-time rotation speed And based on the transmission torque error and transmission speed error Calculate torque ripple values ​​under different load conditions and speed fluctuation value ;

[0031] ;

[0032] S9: Based on torque fluctuation value and speed fluctuation value During the load cycle T Take evenly inside m Each sampling point is used to obtain the torque fluctuation value data corresponding to each sampling point. and speed fluctuation data , For the first m The torque fluctuation value corresponding to each sampling point For the first m Rotational speed fluctuation value corresponding to each sampling point t m For the first m The time corresponding to each sampling point;

[0033] S10: Set the allowable value for torque ripple and allowable value of speed fluctuation Calculate during the test cycle T Transmission performance coefficient of internal rotor drive mechanism f ;

[0034] ;

[0035] in, k The sampling point number, For the first k The torque fluctuation value corresponding to each sampling point For the first k Rotational speed fluctuation value corresponding to each sampling point t k For the first k The time corresponding to each sampling point These are the weighting coefficients for the impact of torque fluctuation and speed fluctuation on rotor transmission performance, respectively, and are generally taken as... ;

[0036] S11: Set the threshold for the transmission performance coefficient. ,like If the rotor transmission mechanism performs well, its transmission performance meets the requirements; otherwise, it does not.

[0037] The beneficial effects of this invention are as follows: This invention provides a working load to the constructed rotor transmission mechanism under test by setting a load motor to simulate the real working environment. Furthermore, this invention further realizes the simulation and testing of the real working environment by outputting a real-time random dynamic load through the load motor. The flip drive motor, as the power source for the flipping and oscillating motion, achieves synchronization between the flipping and rotor rotation through the series connection of the synchronization mechanism. It can perform transmission tests and experiments in various flight attitudes and realize quantitative and qualitative evaluation of transmission performance under dynamic random working conditions, effectively improving the accuracy and rationality of rotor transmission testing and experimentation. Attached Figure Description

[0038] Figure 1 This is a perspective view of the test apparatus for the drive system of a tiltrotor aircraft.

[0039] Figure 2 This is a structural diagram showing the tilt rotor simulation system connected in series with the rollover drive mechanism.

[0040] Figure 3 This is a structural diagram of the flipping limit mechanism.

[0041] Figure 4 This is a diagram showing the connection structure between the sixth drive shaft and the swing box.

[0042] The components include: 1. First drive motor; 2. First speed and torque sensor; 3. T-shaped transmission box; 4. First bevel gear; 5. Intermediate bevel gear; 6. Fourth bevel gear; 7. Fifth bevel gear; 8. First drive shaft; 9. Seventh bevel gear; 10. Second drive shaft; 11. Third drive shaft; 12. Ninth bevel gear; 13. Swing box; 14. Second speed and torque sensor; 15. Load motor; 16. Gearbox; and 17. Third speed and torque sensor. 18. Tilting drive motor; 19. Fourth drive shaft; 20. Fifth drive shaft; 21. Sixth drive shaft; 22. Base plate; 23. Swing rod; 24. Bushing; 25. Bevel gear B; 26. Bevel gear A; 27. Limiting turntable; 28. Collar; 29. ​​Bearing housing; 30. Limiting pin; 31. Third gear; 32. Limiting shaft; 33. Eleventh bevel gear; 34. Extension section; 35. Pin; 36. Swing bearing support; 37. Lug. Detailed Implementation

[0043] The specific embodiments of the present invention are described below to enable those skilled in the art to understand the present invention. However, it should be understood that the present invention is not limited to the scope of the specific embodiments. For those skilled in the art, various changes are obvious as long as they are within the spirit and scope of the present invention as defined and determined by the appended claims. All inventions utilizing the concept of the present invention are protected.

[0044] like Figures 1-4 As shown, a test device for the transmission of a tiltrotor includes a test platform. A tilting drive mechanism and a rotation drive mechanism are respectively installed on the test platform. The tilting 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 mounted on two synchronously tilting bases. The tilting drive mechanism is connected to the two synchronously tilting bases and is used to drive the two bases to tilt synchronously. The synchronization mechanism connects the tiltrotor simulation system, the rotation drive mechanism, and the tilting drive mechanism in series, so that while the tilting drive mechanism drives the bases to tilt, the tiltrotor simulation system and the rotation drive mechanism rotate synchronously.

[0045] In this embodiment, the rotation drive mechanism includes a T-shaped transmission box 3. Two first drive motors 1 are respectively arranged on both sides of the T-shaped transmission box 3. A first speed and torque sensor 2 is arranged between the two first drive motors 1 and the T-shaped transmission box 3. The two ends of the first speed and 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-shaped transmission box 3 through couplings. The output end of the T-shaped transmission box 3 is respectively connected to the load motors 15 on the two bases through the rotor transmission mechanism.

[0046] Both first drive motors 1 can be used as power units for the rotor transmission mechanism. One of the first drive motors 1 is the main drive motor, and the other is the redundant drive motor. When the main drive motor fails, the transmission mechanism is powered normally.

[0047] In this embodiment, a first bevel gear 4 is installed inside the T-shaped transmission box 3. The first bevel gear 4 is mounted on a first input shaft. One end of the first input shaft serves as the first input end of the T-shaped transmission box 3, and a second bevel gear is installed on the other end. Two intermediate bevel gears 5 mesh on both sides of the second bevel gear, and a third bevel gear meshes between the two intermediate bevel gears 5. The second bevel gear, the two intermediate bevel gears 5, and the third bevel gear form an opening shape, and the two intermediate bevel gears 5 are symmetrically arranged on the first bevel gear 4 at the center through an L-shaped axis. The third bevel gear is mounted on a second input shaft, which serves as the second input end of the T-shaped transmission box 3. The first bevel gear 4 meshes with a fourth bevel gear 6 inside the T-shaped transmission box 3, and the fourth bevel gear 6 is mounted on the output end of the T-shaped transmission box 3. Through the design of the T-shaped transmission box 3, the two first drive motors 1 can output power simultaneously and achieve differential power output.

[0048] In this embodiment, the rotor transmission mechanism includes a fifth bevel gear 7 mounted on the output end of the T-shaped transmission box 3. The fifth bevel gear 7 meshes with a sixth bevel gear on the first transmission shaft 8. The first transmission shaft 8 is perpendicular to the output end of the T-shaped transmission box 3. Seventh bevel gears 9 are provided at both ends of the first transmission shaft 8. The seventh bevel gears 9 are respectively located on one end of two second transmission shafts 10, which are perpendicular to the first transmission shaft 8. An eighth bevel gear is provided on the other end of each of the two second transmission shafts 10. The eighth bevel gears on the two second transmission shafts 10 mesh with ninth bevel gears 12 located at one end of two third transmission shafts 11. The other ends of the two third transmission shafts 11 are respectively connected to two tilting rotor simulation systems via a synchronization mechanism. The first transmission shaft 8, the second transmission shaft 10, and the third transmission shaft 11 are mounted on the test platform via bearing seats 29. The first transmission shaft 8, the second transmission shaft 10, and the third transmission shaft 11, along with the associated bevel gears, form an equivalent rotor transmission mechanism, which can effectively simulate the transmission process of a real rotor transmission mechanism.

[0049] In this embodiment, the tilt rotor simulation system includes a load motor 15 mounted on a base. The output end of the load motor 15 is connected to a second speed and torque sensor 14, which is connected to a synchronization mechanism via a coupling. The load motor 15 outputs the load borne by the rotor during flight to simulate the transmission process under load conditions.

[0050] 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 and torque sensor 14 via a coupling. The tenth bevel gear meshes with the eleventh bevel gear 33 located at the other end of the third drive shaft 11. The eleventh bevel gear 33 and the tenth bevel gear are located inside the swing box 13. The third drive shaft 11 extends into the swing box 13 and rotates coaxially with the swing box 13.

[0051] In this embodiment, the flipping drive mechanism includes a flipping drive motor 18, a third speed and torque sensor 17 and a reduction gearbox 16 that are sequentially connected to the flipping drive motor 18. The output end of the reduction gearbox 16 is connected to a fourth drive shaft 19. The end of the fourth drive shaft 19 is 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 bevel gears C and D distributed on both sides of the fourth drive shaft 19. Both bevel gears C and D mesh with bevel gear A26.

[0052] Bevel gears C and D are respectively set at one end of the fifth transmission shaft 20 on both sides, which are coaxial. The other ends of the fifth transmission shaft 20 on both sides are respectively set with a first gear and a second gear. The first gear and the third gear 31 are connected by an intermediate gear, and the second gear meshes with the fourth gear. Bevel gear B25 meshes with 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. The two ends of the sixth transmission shaft 21 are connected to the lugs 37 set on both sides of the swing box 13.

[0053] 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 are respectively distributed on both sides of the swing box 13, and the end of one swing rod 23 is provided on the extension section 34 of the swing bearing support 36 through a bushing 24. The extension section 34 is a hollow structure and is rotatably connected to the bushing 24. The end of the other swing rod 23 is provided with a semi-circular collar 28. The collar 28 is coaxially arranged with the third gear 31 and the fourth gear, and the collar 28 is connected to the third gear 31 and the fourth gear through a pin 35 to rotate synchronously.

[0054] The two side lugs 37 are rotatably connected to the two side swing bearing supports 36, and the lugs 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 swing bearing support 36 and is fixedly connected to one side lug 37. The third gear 31 and the fourth gear are respectively rotatably connected to the extension section 34 of one side swing bearing support 36 through bearings.

[0055] Both bevel gears C and D mesh with bevel gear A26, causing the fifth transmission shafts 20 on both sides to rotate in opposite directions. Therefore, an intermediate gear is placed between the first gear and the third gear 31 to change the direction of rotation 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, providing support. This ensures that the load motor 15 and the swing box 13 remain synchronized during tilting, and the tilting drive motor 18 provides stable power when the swing box 13 and the base plate 22 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 rotate in the same direction and at the same speed.

[0056] In this embodiment, the fourth drive shaft 19 is mounted on the test platform via two bearing seats 29. A flipping limiting mechanism is provided on the fourth drive shaft 19 between the two bearing seats 29. The flipping limiting mechanism includes a limiting turntable 27. Two spaced limiting pins 30 are provided on the side of the limiting turntable 27. One limiting pin 30 is fixed, and the other limiting pin 30 is inserted into a limiting pin hole opened on the limiting turntable 27. At least two limiting pins are arranged side by side in the limiting pin hole. A limiting shaft 32 is provided on the bearing seat 29 to block the limiting pin 30. The limiting shaft 32 cooperates with the limiting pin 30 to limit the tilt angle of the base. The other limiting pin 30 is inserted into different limiting pin holes to adjust the tilt angle range of the base.

[0057] A test method for the above-mentioned tiltrotor engine transmission test device is provided, comprising the following steps:

[0058] S1: The first drive motor 1 or the second drive motor starts, outputting the set torque. and rotational speed The first speed and torque sensor 2 collects the actual torque output by the first drive motor 1 or the second drive motor under zero-load conditions. and rotational speed ;

[0059] S2: The second speed and torque sensor 14 collects the torque under zero-load conditions. and rotational speed Calculate the transmission torque error and transmission speed error ;

[0060] S3: Constructing a wind speed power spectrum model under wind load turbulent random fluctuations;

[0061] ;

[0062] in, f For frequency, For frequency fluctuation coefficient, frequency coefficient Pick Random numbers between The turbulence length is taken as 50-100m for low-altitude flight. V The target wind speed (m / s) for the experiment. The variance of longitudinal wind speed based on turbulence intensity. The power of the turbulent wind speed in the experiment, T For the load cycle, N The number of times the load is applied within the load cycle; when applying wind load power, this invention introduces a sine function to randomize the frequency and calculate the wind load at random frequencies in order to simulate random wind loads.

[0063] S4: Set a fixed turbulent wind speed power, and calculate the power during the load cycle based on the wind speed power spectrum model. T Different times within t fluctuating wind speed value And based on fluctuating wind speed values Calculate load cycle T Load force at different times ;

[0064] ;

[0065] in, air density, c The rotor chord length set for the experiment, r The rotor radius is... The drag generated by the rotor, U This refers to the rotor rotation speed;

[0066] S5: Based on load capacity Calculate the rotor during the load cycle T Load torque at different times ;

[0067] ;

[0068] in, The length of the rotor's load unit;

[0069] S6: Start the load motor 15 to load the dynamic load, so that the torque data collected by the second speed and torque sensor 14 meets the load torque. And obtain the real-time rotation speed. ;

[0070] S7: The flip drive motor 18 drives the swing box 13 and the base to reciprocate at a fixed rate;

[0071] S8: The first speed and torque sensor 2 collects the load torque. Real-time torque under certain conditions and real-time rotation speed And based on the transmission torque error and transmission speed error Calculate torque ripple values ​​under different load conditions and speed fluctuation value ;

[0072] ;

[0073] S9: Based on torque fluctuation value and speed fluctuation value During the load cycleT Take evenly inside m Each sampling point is used to obtain the torque fluctuation value data corresponding to each sampling point. and speed fluctuation data , For the first m The torque fluctuation value corresponding to each sampling point For the first m Rotational speed fluctuation value corresponding to each sampling point t m For the first m The time corresponding to each sampling point;

[0074] S10: Set the allowable value for torque ripple and allowable value of speed fluctuation Calculate during the test cycle T Transmission performance coefficient of internal rotor drive mechanism f ;

[0075] ;

[0076] in, k The sampling point number, For the first k The torque fluctuation value corresponding to each sampling point For the first k Rotational speed fluctuation value corresponding to each sampling point t k For the first k The time corresponding to each sampling point These are the weighting coefficients for the impact of torque fluctuation and speed fluctuation on rotor transmission performance, respectively, and are generally taken as... ;

[0077] S11: Set the threshold for the transmission performance coefficient. ,like If the rotor transmission mechanism performs well, its transmission performance meets the requirements; otherwise, it does not.

[0078] This invention simulates a real working environment by setting a load motor 15 to provide a working load for the constructed rotor transmission mechanism under test. Furthermore, the invention further simulates and tests the real working environment by outputting a real-time random dynamic load through the load motor 15. The flip drive motor 18, as the power source for the flipping and oscillating motion, achieves synchronization between flipping and rotor rotation through a series synchronization mechanism. This allows for transmission tests and experiments in various flight attitudes and enables 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 apparatus for the transmission of a tiltrotor aircraft, characterized in that, The test platform includes a tilting drive mechanism and a rotation drive mechanism. The tilting drive mechanism and the rotation drive mechanism are connected by a synchronization mechanism. The rotation drive mechanism is used to synchronously drive two tilting rotor simulation systems to rotate. The two tilting rotor simulation systems are respectively mounted on two synchronously tilting bases. The tilting drive mechanism is connected to the two synchronously tilting bases and is used to drive the two bases to tilt synchronously. The synchronization mechanism connects the tilting rotor simulation system, the rotation drive mechanism, and the tilting drive mechanism in series, so that while the tilting drive mechanism drives the base to tilt, the tilting rotor simulation system and the rotation drive mechanism rotate synchronously. The flipping drive mechanism includes a flipping drive motor, a third speed and torque sensor and a reduction gearbox that are sequentially connected to the flipping drive motor. The output end of the reduction gearbox is connected to a fourth drive shaft. The end of the fourth drive shaft is provided with bevel gear A and bevel gear B in sequence. A gap is provided between bevel gear A and bevel gear B to accommodate bevel gear C and bevel gear D distributed on both sides of the fourth drive shaft. Both bevel gear C and bevel gear D mesh with bevel gear A. The bevel gear C and bevel gear D are respectively set at one end of the fifth transmission shaft on both sides. The other ends of the fifth transmission shaft on both sides are respectively set with a first gear and a second gear. The first gear and the third gear are connected by an intermediate gear, and the second gear meshes with the fourth gear. The bevel gear B meshes with the bevel gear E set in the middle of the sixth transmission shaft. The sixth transmission shaft is coaxial with the two third transmission shafts. The two ends of the sixth transmission shaft are connected to the lugs set on both sides of the swing box. The base includes a base plate, and swing rods are respectively provided on both sides of the base plate. The swing rods are distributed on both sides of the swing box, and the end of one swing rod is provided on the extension section of the swing bearing support through a bushing. The extension section is a hollow structure and is rotatably connected to the bushing. The end of the other swing rod is provided with a semi-circular collar. The collar is coaxially arranged with the third gear and the fourth gear. The collar is connected to the third gear and the fourth gear through a pin and rotates 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 one of the swing bearing supports and is fixedly connected to one of the lugs on one side. The third gear and the fourth gear are rotatably connected to the extension section of one swing bearing support through bearings.

2. The test apparatus for tiltrotor engine transmission according to claim 1, characterized in that, The rotation drive mechanism includes a T-shaped transmission box, with two first drive motors respectively arranged on both sides of the T-shaped transmission box. A first speed and torque sensor is arranged between the two first drive motors and the T-shaped transmission box, and the two ends of the first speed and 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-shaped transmission box through couplings. The output end of the T-shaped transmission box is respectively connected to the load motors on the two bases through a rotor transmission mechanism.

3. The test apparatus for tiltrotor engine transmission according to claim 2, characterized in that, The T-shaped transmission box contains a first bevel gear mounted on a first input shaft. One end of the first input shaft serves as the first input end of the T-shaped transmission box, and the other end is equipped with a second bevel gear. Two intermediate bevel gears mesh on both sides of the second bevel gear, and a third bevel gear meshes between the two intermediate bevel gears. The second bevel gear, the two intermediate bevel gears, and the third bevel gear form an opening, and the two intermediate bevel gears are symmetrically arranged on the first bevel gear at the center via an L-shaped axis. The third bevel gear is mounted on a second input shaft, which serves as the second input end of the T-shaped transmission box. The first bevel gear meshes with a fourth bevel gear inside the T-shaped transmission box, and the fourth bevel gear is mounted on the output end of the T-shaped transmission box.

4. The test apparatus for tiltrotor engine transmission according to claim 3, characterized in that, The rotor transmission mechanism includes a fifth bevel gear mounted on the output end of a T-shaped transmission box. The fifth bevel gear meshes with a sixth bevel gear on a first transmission shaft. The first transmission shaft is perpendicular to the output end of the T-shaped transmission box. Seventh bevel gears are provided at both ends of the first transmission shaft. The seventh bevel gears at both ends are respectively located on one end of two second transmission shafts. The second transmission shafts are perpendicular to the first transmission shaft. An eighth bevel gear is provided on the other end of each of the two second transmission shafts. The eighth bevel gears on the two second transmission shafts mesh with ninth bevel gears located at one end of two third transmission shafts. The other ends of the two third transmission shafts are respectively connected to the two tilting rotor simulation systems via a synchronization mechanism. The first, second, and third transmission shafts are mounted on the test platform via bearing seats.

5. The test apparatus for tiltrotor engine transmission according to claim 4, characterized in that, The tilt rotor simulation system includes a load motor mounted on a base. The output end of the load motor is connected to a second speed and torque sensor. 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 and torque sensor via a coupling. The tenth bevel gear meshes with the eleventh bevel gear located at the other end of the third drive shaft. The eleventh bevel gear and the tenth bevel gear are located inside the swing box. The third drive shaft extends into the swing box and rotates coaxially with the swing box.

6. The test apparatus for tiltrotor engine transmission according to claim 5, characterized in that, The fourth drive shaft is mounted on the test platform via two bearing seats. A tilting and limiting mechanism is provided on the fourth drive shaft between the two bearing seats. The tilting and limiting mechanism includes a limiting turntable. Two spaced limiting pins are provided on the side of the limiting turntable. One limiting pin is fixed, and the other limiting pin is inserted into a limiting pin hole opened on the limiting turntable. At least two limiting pins are arranged side by side in the limiting pin hole. A limiting shaft is provided on the bearing seat to block the limiting pin. The limiting shaft and the limiting pin cooperate to limit the tilt angle of the base. The other limiting pin is inserted into different limiting pin holes to adjust the tilt angle range of the base.

7. A test method for the test apparatus of the tiltrotor engine transmission as described in claim 6, characterized in that, Includes the following steps: S1: The first or second drive motor starts and outputs the set torque. and rotational speed The first speed and torque sensor collects the actual torque output by the first or second drive motor under zero-load conditions. and rotational speed ; S2: The second speed and torque sensor collects torque under zero-load conditions. and rotational speed Calculate the transmission torque error and transmission speed error ; S3: Constructing a wind speed power spectrum model under wind load turbulent random fluctuations; ； in, f For frequency, For frequency fluctuation coefficient, frequency coefficient Pick Random numbers between For turbulence length, V The target wind speed for the test, The variance of longitudinal wind speed based on turbulence intensity. The power of the turbulent wind speed in the experiment, T For the load cycle, N The number of times the load is applied within a load cycle; S4: Set a fixed turbulent wind speed power, and calculate the power during the load cycle based on the wind speed power spectrum model. T Different times within t fluctuating wind speed value And based on fluctuating wind speed values Calculate load cycle T Load force at different times ; ； in, air density, c The rotor chord length set for the experiment, r The rotor radius is... The drag generated by the rotor, U This refers to the rotor rotation speed; S5: Based on load capacity Calculate the rotor during the load cycle T Load torque at different times ; ； in, The length of the rotor's load unit; S6: Start the load motor to apply the dynamic load, ensuring that the torque data collected by the second speed and torque sensor meets the load torque requirements. And obtain the real-time rotation speed. ; S7: The flip drive motor drives the swing box and base to reciprocate at a fixed rate; S8: The first speed and torque sensor collects data on the load torque. Real-time torque under certain conditions and real-time rotation speed And based on the transmission torque error and transmission speed error Calculate torque ripple values ​​under different load conditions and speed fluctuation value ; ； S9: Based on torque fluctuation value and speed fluctuation value During the load cycle T Take evenly inside m Each sampling point is used to obtain the torque fluctuation value data corresponding to each sampling point. and speed fluctuation data , For the first m The torque fluctuation value corresponding to each sampling point For the first m Rotational speed fluctuation value corresponding to each sampling point t m For the first m The time corresponding to each sampling point; S10: Set the allowable value for torque ripple and allowable value of speed fluctuation Calculate during the test cycle T Transmission performance coefficient of internal rotor drive mechanism f ; ； in, k The sampling point number, For the first k The torque fluctuation value corresponding to each sampling point For the first k Rotational speed fluctuation value corresponding to each sampling point t k For the first k The time corresponding to each sampling point These are the weighting coefficients for the impact of torque fluctuation and speed fluctuation on rotor transmission performance, respectively. S11: Set the threshold for the transmission performance coefficient. ,like If the rotor transmission mechanism performs well, its transmission performance meets the requirements; otherwise, it does not.

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