Engine Gear Dynamic Stress Measurement and Testing System

Abstract

This invention discloses an engine gear dynamic stress measurement and testing system, comprising: a mounting housing, a gear to be tested rotatably mounted on the mounting housing, slip ring actuators and a drive measurement system respectively disposed on both sides of the gear to be tested, and an air supply loading system. The drive measurement system is connected to the gear to be tested to drive the gear to be tested and simultaneously measure the torque and speed of the gear to be tested during the test. The slip ring actuators are connected to the gear to be tested to measure the dynamic stress of the gear to be tested. The air supply loading system is partially connected to the gear to be tested, and the remaining part is located on the outside of the gear to be tested, to spray high-pressure air of a specific pressure onto the tooth surface of the gear to be tested at a specific angle in the opposite direction of the rotation of the gear to be tested, so as to form an excitation consistent with the meshing frequency of the actual gear. The engine gear dynamic stress measurement and testing system of this invention has high efficiency and high reliability in measuring the dynamic stress of the gear to be tested, which can greatly improve the testing efficiency and accelerate the engine development progress.

Description

Technical Field

[0001] This invention relates to the field of gear dynamic stress measurement, and in particular, to a test system for measuring the dynamic stress of engine gears. Background Technology

[0002] Aero engines operate over a wide speed range, making it difficult to completely avoid designing gears to resonate at all engine operating speeds. While gear modal analysis can calculate the resonant frequency and speed, it cannot determine the actual dynamic stress at the resonant speed, thus failing to accurately assess the risk of resonant failure at that speed. Currently, to verify whether gears will experience resonant failure, dynamic stress measurement tests are often conducted on the gears during engine testing or in component testing equipment.

[0003] 1) There are several disadvantages to conducting dynamic stress measurement tests on the entire engine:

[0004] a) Currently, the dynamic stress measurement of gears is mainly carried out using slip ring actuators. This equipment requires the engine to provide a certain installation space. However, the engine has a compact structure and it is often difficult to provide enough installation space for slip ring actuators. Therefore, the engine needs to be modified a lot to complete the dynamic stress measurement of a gear. This requires testing and modification of engine components, which takes a long time to test a gear. Moreover, in many cases, it is difficult to test and modify the engine, which means that the gear that needs to be measured for dynamic stress cannot be measured.

[0005] b) Dynamic stress measurement on the engine requires that the structure of engine components has been basically finalized. If the dynamic stress measurement test shows that a certain gear has excessive dynamic stress and is at risk of resonance failure, then a major structural adjustment of the gear is often required. Engine design is holistic, and a change in the structural design of one part often requires a series of corresponding adjustments to other components, which greatly delays the engine development progress.

[0006] 2) Performing dynamic stress measurement tests on a component testing machine has the following disadvantages:

[0007] Compared to the whole machine, dynamic stress measurement tests on components are relatively easier to modify and test. However, to simulate the working load of the whole machine, an additional load is required. Currently, gear dynamic stress tests are performed using loads with real accessories or load motors. Both real accessories and load motors have speed limits, which are generally difficult to match with the specific gear's working speed. A dedicated reducer needs to be designed for speed matching, making the system more complex, with a longer processing cycle, higher cost, and lower testing efficiency. Due to the addition of many auxiliary test components, the test failure rate will increase significantly. At the same time, corresponding installation space and mounting bases are required for testing equipment such as slip ring current collectors, which often brings great inconvenience to design and processing, making the testing equipment more complex. Summary of the Invention

[0008] This invention provides an engine gear dynamic stress measurement test system to solve the technical problems of existing stress measurement tests, such as the need to modify engine parts, complex test system structure, long measurement cycle, and low test efficiency.

[0009] The technical solution adopted in this invention is as follows:

[0010] An engine gear dynamic stress measurement and testing system includes: a mounting housing, a gear to be tested rotatably mounted on the mounting housing, slip ring actuators and a drive measurement system respectively disposed on both sides of the gear to be tested, and an air supply loading system; the drive measurement system is connected to the gear to be tested along the axis to drive the gear to be tested according to the actual engine speed and torque, and simultaneously measure the torque and speed of the gear to be tested during the test process; the slip ring actuators are connected to the gear to be tested along the axis to measure the dynamic stress of the gear to be tested; the air supply loading system is partially connected to the gear to be tested, and the remaining part is located on the outside of the gear to be tested, to spray high-pressure air of a specific pressure onto the tooth surface of the gear to be tested at a specific angle in the opposite direction of the rotation of the gear to be tested, so as to form an excitation consistent with the meshing frequency of the actual gear.

[0011] Furthermore, the gear under test includes a gear disk and a gear shaft coaxially fixed to the gear disk, the gear shaft being rotatably mounted on the housing; the air supply loading system includes an air supply device for supplying high-pressure air required for the test, a nozzle connected to the air supply device, and an axial force measuring component mounted on the outer circle of the gear shaft; the nozzle is used to spray high-pressure air at a specific pressure at a specific angle in the opposite direction of the rotation of the gear under test onto the tooth surface of the gear under test, so as to simulate the load experienced by the gear under test during actual meshing; the axial force measuring component is used to measure the axial force experienced by the gear under test during the test, thereby guiding the adjustment of the nozzle spray angle so that the actual axial force experienced by the gear under test matches the theoretical calculation value.

[0012] Furthermore, if the gear under test is a cylindrical gear, the specific angle of the nozzle spray is α = 0; if the gear under test is a helical gear, the specific angle of the nozzle spray is α1 equal to the pitch circle helix angle β1 of the helical gear; if the gear under test is a bevel gear, the specific angle of the nozzle spray is α2 equal to the pitch circle helix angle β2 of the bevel gear.

[0013] Furthermore, when the gear under test is a cylindrical gear or a helical gear, the cross-section of the nozzle orifice is square. Let the tooth height of the cylindrical gear and the helical gear be H, the tooth width be B, the meshing overlap of the gear teeth be ε, the height of the nozzle be h, and the width be b. Then, when h = (ε-1)H and b = B, the area sprayed by the nozzle can simulate the single and double meshing areas of the real gear during the meshing process.

[0014] Furthermore, let the torque transmitted by the cylindrical gear be T, the pitch circle diameter of the cylindrical gear be D, and the specific pressure that the nozzle needs to supply be P, then: α = 0.

[0015] Furthermore, let the torque transmitted by the helical gear be T1, the pitch circle diameter of the helical gear be D1, and the specific pressure required by the nozzle be P1, then: α1 = β1.

[0016] Furthermore, when the gear under test is a bevel gear, the cross-section of the nozzle orifice is an isosceles trapezoid. Let: the tooth height at the small end of the bevel gear be H1, the tooth height at the large end be H2, the tooth width be B1, the tooth meshing overlap be ε1, the height at the small end of the nozzle orifice be h1, the height at the large end be h2, and the width be b1. Then: when h1 = (ε1-1)H1, h2 = (ε1-1)H2, and b1 = B1, the area sprayed by the nozzle can simulate the single and double meshing areas of a real gear during the meshing process.

[0017] Furthermore, let the torque transmitted by the bevel gear be T2, the pitch circle diameter of the bevel gear be D2, and the specific pressure required by the nozzle be P2, then: α2 = β2.

[0018] Furthermore, the drive measurement system includes an electric motor for rotating the gear under test according to the actual speed and torque of the engine, a torque and speed measuring instrument for measuring the torque and speed transmitted during the test of the gear under test, and a splined shaft, a first diaphragm coupling, and a second diaphragm coupling that serve as connections and power transmission components. The electric motor, the torque and speed measuring instrument, and the splined shaft are arranged sequentially at intervals along the power transmission direction. The first diaphragm coupling is axially connected between the electric motor and the torque and speed measuring instrument, and the second diaphragm coupling is axially connected between the torque and speed measuring instrument and the splined shaft. The other end of the splined shaft is coaxially connected to the gear shaft.

[0019] Furthermore, the engine gear dynamic stress measurement test system also includes a drive shaft, one end of which is axially fixedly connected to the gear shaft, and the other end of which is connected to a slip ring actuator; the axial force measuring assembly includes two axial force measuring rings, which are sequentially and spaced apart on the outer circle of the gear shaft along the axial direction of the gear shaft, and both are located inside the casing.

[0020] The present invention has the following beneficial effects:

[0021] The engine gear dynamic stress measurement test system of this invention uses high-pressure gas to spray onto the tooth surface of the gear under test, thereby forming a load. The high-pressure gas injection and the rotation of the gear under test generate excitation at the same frequency as when a real gear is meshing, inducing the gear's modal vibration. The dynamic stress of the gear spokes can then be measured via a slip ring actuator, identifying dangerous vibration modes. This method offers high efficiency and reliability in measuring the dynamic stress of the gear under test. Furthermore, this invention employs a novel loading method using a gas-supply loading system. Compared to performing dynamic stress measurement tests on gears during engine testing, this method eliminates the need for a separate loading device with gears and does not require connection to the engine during testing. Therefore, it avoids the need for testing, modifying, or structurally adjusting engine components, significantly improving testing efficiency and accelerating engine development. Compared to component testing equipment that uses real accessories or load motors to measure gear dynamic stress, this method reduces the need for real accessories or load motors, greatly simplifying the test structure, providing more installation space for the testing device, and eliminating the need for a dedicated reducer for speed matching. This simplifies the structure considerably, resulting in high testing efficiency and a low failure rate.

[0022] In addition to the objectives, features, and advantages described above, the present invention has other objectives, features, and advantages. The invention will now be described in further detail with reference to the figures. Attached Figure Description

[0023] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0024] Figure 1 This is a schematic diagram of the engine gear dynamic stress measurement and testing system according to a preferred embodiment of the present invention;

[0025] Figure 2 This is a schematic diagram of nozzles used for cylindrical gears and helical gears;

[0026] Figure 3 This is a schematic diagram of a nozzle for bevel gears.

[0027] Legend

[0028] 10. Mounting housing; 20. Gear to be tested; 21. Gear disc; 22. Gear shaft; 30. Slip ring actuator; 40. Drive measurement system; 41. Electric motor; 42. Torque and speed measuring instrument; 43. Splined shaft; 44. First diaphragm coupling; 45. Second diaphragm coupling; 50. Air supply loading system; 51. Air supply device; 52. Nozzle; 531. Axial force measuring ring; 60. Drive shaft. Detailed Implementation

[0029] The embodiments of the present invention will be described in detail below with reference to the accompanying drawings. However, the present invention can be implemented in many different ways as defined and covered below.

[0030] Reference Figure 1 A preferred embodiment of the present invention provides an engine gear dynamic stress measurement test system, comprising: a mounting housing 10, a gear 20 to be tested rotatably mounted on the mounting housing 10, slip ring actuators 30 disposed on both sides of the gear 20 to be tested, a drive measurement system 40, and an air supply loading system 50. The drive measurement system 40 is connected to the gear 20 to be tested along an axis to drive the gear 20 to be tested according to the actual engine speed and torque, and simultaneously measure the torque and speed of the gear 20 to be tested during the test. The slip ring actuators 30 are connected to the gear 20 to be tested along an axis to measure the dynamic stress of the gear 20 to be tested. The air supply loading system 50 is partially connected to the gear 20 to be tested, with the remaining portion located on the outside of the gear 20 to inject high-pressure air of a specific pressure onto the tooth surface of the gear 20 to be tested at a specific angle in the opposite direction of the gear 20's rotation, thereby forming an excitation consistent with the meshing frequency of the actual gear.

[0031] When the engine gear dynamic stress measurement test system of the present invention is working, the drive measurement system 40 drives the gear under test 20 according to the actual speed and torque of the turbine engine; then the air supply loading system 50 is turned on, which sprays high-pressure gas of a specific pressure onto the tooth surface of the gear under test 20 at a specific angle in the opposite direction of the rotation of the gear under test 20, thereby forming a load. At the same time, the drive measurement system 40 monitors the speed of the gear under test 20 and the load formed by the high-pressure gas in real time; finally, the dynamic stress on the gear under test 20 is measured by the slip ring actuator 30.

[0032] The engine gear dynamic stress measurement test system of the present invention uses high-pressure gas to spray onto the tooth surface of the gear 20 under test, thereby forming a load. The high-pressure gas injection and the rotation of the gear under test generate an excitation at the same frequency as when the gear is meshing, inducing the gear's modal vibration. The dynamic stress of the gear spokes can then be measured via the slip ring actuator 30, and dangerous vibration modes can be identified. The dynamic stress measurement of the gear under test is highly efficient and reliable. Furthermore, the present invention employs a novel loading method using a gas supply loading system 50. Compared to performing dynamic stress measurement tests on gears during engine testing, this method eliminates the need for a loading device with gears and does not require connection to the engine test. Therefore, it eliminates the need for testing, modification, or structural adjustments to engine components, greatly improving testing efficiency and accelerating engine development. Compared to component testing equipment that uses real accessories or load motors to measure gear dynamic stress, this method reduces the need for real accessories or load motors, significantly simplifying the test structure, providing more installation space for the testing device, and eliminating the need for a dedicated reducer for speed matching. This greatly simplifies the structure, resulting in high testing efficiency and a low failure rate.

[0033] Optionally, such as Figure 1 As shown, the gear under test 20 includes a gear disk 21 and a gear shaft 22 coaxially fixed to the gear disk 21. The gear shaft 22 is rotatably mounted on the housing. The air supply loading system 50 includes an air supply device 51 for supplying high-pressure air required for the test, a nozzle 52 connected to the air supply device 51, and an axial force measuring component mounted on the outer circle of the gear shaft 22. The nozzle 52 is used to spray high-pressure air at a specific pressure at a specific angle in the opposite direction of rotation of the gear under test 20 onto the tooth surface of the gear under test 20 to simulate the load experienced by the gear under test 20 during actual meshing. The axial force measuring component is used to measure the axial force experienced by the gear under test 20 during the test, thereby guiding the adjustment of the spray angle of the nozzle 52 so that the actual axial force experienced by the gear under test 20 matches the theoretically calculated value.

[0034] In this optional scheme, in order to generate an excitation with a frequency consistent with the actual gear meshing frequency when high-pressure gas is injected onto the gear tooth surface, thereby improving the accuracy of the test measurement, this invention, after long-term theoretical research and a large number of experimental verifications and adjustments, found that: when the gear under test 20 is a cylindrical gear, and the specific angle α of the nozzle 52 is 0, the actual axial force on the gear under test 20 matches the theoretical calculation value; similarly, when the gear under test 20 is a helical gear, and the specific angle α1 of the nozzle 52 is equal to the pitch circle helix angle β1 of the helical gear, the actual axial force on the gear under test 20 matches the theoretical calculation value; similarly, when the gear under test 20 is a bevel gear, and the specific angle α2 of the nozzle 52 is equal to the pitch circle helix angle β2 of the bevel gear, the actual axial force on the gear under test 20 matches the theoretical calculation value.

[0035] In this invention, after long-term research on gear vibration, it was discovered that gear vibration is mainly caused by resonance due to the number of meshing excitations at the resonant speed. If the number of teeth on the gear is z, and the resonant speed is n (r / min), then the meshing frequency f is: f = n / 60*z. In this invention, during the experiment, the gear under test 20 rotates while the nozzle remains stationary, and the gear under test receives an impact load from the high-pressure gas for each tooth it rotates. One revolution receives z impact loads. When the gear reaches the resonant speed n, the frequency of the impact load is n / 60*z, which is consistent with the meshing frequency generated during actual gear meshing. Therefore, this invention can achieve an impact load consistent with the actual gear meshing frequency. The load magnitude is controlled according to the gear tooth height, tooth width, and jet pressure.

[0036] Furthermore, the nozzle orifice size needs to be designed based on the gear's tooth height H, tooth width B, and meshing overlap ratio ε. In this invention, when the gear 20 to be tested is a cylindrical gear or a helical gear, the cross-section of the nozzle 52 orifice is designed to be square, such as... Figure 2 As shown, the height of the nozzle is h and the width is b. Then, when h = (ε-1)H and b = B, the area sprayed by nozzle 52 can simulate the single and double meshing areas of a real gear during meshing. For example, if the gear overlap ratio is 1.3, it means that the single-tooth meshing area is 0.7 and the double-tooth meshing area is 0.6. In this case, if the nozzle height is set to 0.3H and the nozzle width is consistent with the tooth width, then in the 0.6 area, the double teeth will be subjected to jet impact load, and in the 0.7 area, the single tooth will be subjected to jet impact load, thus simulating the real single and double meshing areas of the gear and achieving consistency with the real gear meshing situation.

[0037] In this invention, the gear meshing process is simulated by adjusting the size of the nozzle orifice, thereby simulating gear meshing excitation. The injection of high-pressure gas and the rotation of the gear generate excitation at the same frequency as actual gear meshing, inducing the gear's modal vibration. Dynamic stress measurement tests are then conducted to measure the dynamic stress of the gear spokes and identify dangerous vibration modes. This invention, by setting the nozzle size, can simulate the frequency and excitation of actual gear meshing, ensuring that the resonance at the resonant frequency is consistent with that of actual gear meshing. Furthermore, compared to actual gear meshing, one gear is eliminated, significantly simplifying the test piece structure and providing more installation space for the testing device, facilitating testing. Simultaneously, based on measured data from the drive measurement system and axial force measuring component, the nozzle angle is adjusted to match the actual load during gear meshing, thereby improving the accuracy of the test measurement.

[0038] Furthermore, let the torque transmitted by the cylindrical gear be T, the pitch circle diameter of the cylindrical gear be D, and the specific pressure required to be supplied by nozzle 52 be P, then:

[0039] α = 0.

[0040] Let the torque transmitted by the helical gear be T1, the pitch circle diameter of the helical gear be D1, and the specific pressure required to be supplied by nozzle 52 be P1, then:

[0041] α1 = β1.

[0042] This invention employs a novel gear dynamic stress measurement scheme to achieve high efficiency and reliability in measuring gear dynamic stress. Compared to the existing patent CN113203562A, where the air supply device simply provides a load and cannot generate an excitation consistent with the actual gear meshing frequency, this invention can simulate the actual gear meshing frequency. By adjusting the size of the nozzle, it provides the gear being blown with an excitation at a meshing frequency, and by adjusting the nozzle size, it controls the load P, thus achieving consistency with the actual working conditions of the gear.

[0043] Similarly, this invention also requires designing the nozzle orifice size based on the gear's tooth height H, tooth width B, and meshing overlap ratio ε. In this invention, when the gear to be tested 20 is a bevel gear, the cross-section of the nozzle 52 orifice is designed to be an isosceles trapezoid, such as... Figure 3 As shown, let the tooth height at the small end of the bevel gear be H1, the tooth height at the large end be H2, the tooth width be B1, and the tooth contact ratio be ε1. Let the height at the small end of the nozzle be h1, the height at the large end be h2, and the width be b1. Then:

[0044] When h1 = (ε1-1)H1, h2 = (ε1-1)H2, and b1 = B1, the area sprayed by nozzle 52 can simulate the single and double meshing areas of real gears during meshing. In this invention, the design principle of the nozzle orifice corresponding to the bevel gear is the same as the design principle of the nozzle orifice corresponding to the cylindrical gear and helical gear mentioned above, and will not be repeated here.

[0045] Furthermore, let the torque transmitted by the bevel gear be T2, the pitch circle diameter of the bevel gear be D2, and the specific pressure required to be supplied by the nozzle 52 be P2, then:

[0046] α2 = β2. This invention can simulate the meshing frequency of real gears. By adjusting the size of the nozzle, it can provide the gear being blown with an excitation at a meshing frequency, and by adjusting the size of the nozzle, it can control the load P, thus achieving the goal of being consistent with the actual working conditions of the gears.

[0047] Optionally, such as Figure 1As shown, the drive measurement system 40 includes a motor 41 for rotating the gear 20 under test according to the actual engine speed and torque, a torque and speed measuring device 42 for measuring the torque and speed transmitted by the gear 20 under test during the test, and a splined shaft 43, a first diaphragm coupling 44, and a second diaphragm coupling 45 that serve as connections and power transmission components. The motor 41, torque and speed measuring device 42, and splined shaft 43 are arranged sequentially at intervals along the power transmission direction. The first diaphragm coupling 44 is axially connected between the motor 41 and the torque and speed measuring device 42, and the second diaphragm coupling 45 is axially connected between the torque and speed measuring device 42 and the splined shaft 43. The other end of the splined shaft 43 is coaxially connected to the gear shaft 22. The overall structure of the system of this invention is simple, and the power transmission path is clear.

[0048] Optionally, such as Figure 1 As shown, the engine gear dynamic stress measurement test system also includes a drive shaft 60, one end of which is axially fixedly connected to the gear shaft 22, and the other end is connected to a slip ring actuator 30. The axial force measuring assembly includes two axial force measuring rings 531, which are sequentially and spaced apart on the outer circle of the gear shaft 22 along the axial direction of the gear shaft 22, and are both located inside the housing.

[0049] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A dynamic stress measurement and testing system for engine gears, characterized in that, include: Mounting housing (10), rotating gear under test (20) mounted on mounting housing (10), slip ring actuators (30) and driving measurement system (40) located on both sides of gear under test (20), and air supply loading system (50). The drive measurement system (40) is connected to the gear under test (20) along the axis to drive the gear under test (20) according to the actual speed and torque of the engine, and at the same time measure the torque and speed of the gear under test (20) during the test process. The slip ring actuator (30) is connected to the gear (20) to be tested along the axis to measure the dynamic stress of the gear (20); The air supply loading system (50) is partially connected to the gear under test (20), and the remaining part of the structure is located on the outside of the gear under test (20) to spray high-pressure air of a specific pressure onto the tooth surface of the gear under test (20) in the opposite direction of the rotation of the gear under test (20) at a specific angle, so as to form an excitation consistent with the meshing frequency of the real gear. The gear to be tested (20) includes a gear disk (21) and a gear shaft (22) fixed coaxially with the gear disk (21). The gear shaft (22) is rotatably mounted on the housing. The air supply loading system (50) includes an air supply device (51) for supplying high-pressure air required for the test, a nozzle (52) connected to the air supply device (51), and an axial force measuring component mounted on the outer circle of the gear shaft (22). The nozzle (52) is used to spray high-pressure air of a specific pressure at a specific angle in the opposite direction of the rotation of the gear to be tested (20) onto the tooth surface of the gear to be tested (20) to simulate the load on the gear to be tested (20) when it is actually meshing. The axial force measuring component is used to measure the axial force on the gear to be tested (20) during the test, and then guide the adjustment of the spray angle of the nozzle (52) so that the actual axial force on the gear to be tested (20) matches the theoretical calculation value.

2. The engine gear dynamic stress measurement and testing system according to claim 1, characterized in that, The gear under test (20) is a cylindrical gear, and the nozzle (52) sprays at a specific angle. ; The gear under test (20) is a helical gear, and the nozzle (52) sprays at a specific angle. Equal to the pitch circle helix angle of a helical gear ; The gear under test (20) is a bevel gear, and the nozzle (52) sprays at a specific angle. Equal to the pitch circle helix angle of the bevel gear .

3. The engine gear dynamic stress measurement and testing system according to claim 2, characterized in that, When the gear to be tested (20) is a cylindrical gear or a helical gear, the cross-section of the nozzle (52) is square. Let: Given that the tooth height of the cylindrical gear and helical gear is H, the tooth width is B, and the meshing overlap ratio is ε, and the height of the nozzle is h and the width is b, then: when , At that time, the area sprayed by the nozzle (52) can simulate the single and double meshing areas of real gears during the meshing process.

4. The engine gear dynamic stress measurement and testing system according to claim 3, characterized in that, Let the torque transmitted by the cylindrical gear be T, the pitch circle diameter of the cylindrical gear be D, and the specific pressure required by the nozzle (52) be P, then: ， 。 5. The engine gear dynamic stress measurement and testing system according to claim 3, characterized in that, Let the torque transmitted by the helical gear be... The pitch circle diameter of the helical gear is The specific pressure that the nozzle (52) needs to supply is ,but: ， 。 6. The engine gear dynamic stress measurement and testing system according to claim 2, characterized in that, When the gear to be tested (20) is a bevel gear, the cross-section of the nozzle (52) orifice is an isosceles trapezoid. Let: The tooth height at the small end of the bevel gear is The height of the large end teeth is Tooth width is Gear tooth meshing overlap degree is The height of the small end of the nozzle is The height of the large end is Width is ,but: when , , At that time, the area sprayed by the nozzle (52) can simulate the single and double meshing areas of real gears during the meshing process.

7. The engine gear dynamic stress measurement and testing system according to claim 6, characterized in that, Let the torque transmitted by the bevel gear be... The pitch circle diameter of the bevel gear is The specific pressure that the nozzle (52) needs to supply is ,but: ， 。 8. The engine gear dynamic stress measurement and testing system according to claim 1, characterized in that, The drive measurement system (40) includes an electric motor (41) for rotating the gear under test (20) according to the actual speed and torque of the engine, a torque and speed measuring device (42) for measuring the torque and speed transmitted by the gear under test (20) during the test, and a spline shaft (43), a first diaphragm coupling (44), and a second diaphragm coupling (45) for connecting and transmitting power. The electric motor (41), torque and speed measuring device (42) and spline shaft (43) are arranged in sequence at intervals along the power transmission direction. The first diaphragm coupling (44) is axially connected between the electric motor (41) and the torque and speed measuring device (42). The second diaphragm coupling (45) is axially connected between the torque and speed measuring device (42) and the spline shaft (43). The other end of the spline shaft (43) is coaxially connected to the gear shaft (22).

9. The engine gear dynamic stress measurement and testing system according to claim 1, characterized in that, The engine gear dynamic stress measurement test system also includes a drive shaft (60), one end of which is axially fixedly connected to a gear shaft (22), and the other end is connected to a slip ring actuator (30). The axial force measuring assembly includes two axial force measuring rings (531). The two axial force measuring rings (531) are sequentially and spaced apart on the outer circle of the gear shaft (22) along the axial direction of the gear shaft (22), and both are located inside the casing.

Images