Eccentricity measuring device and method

Abstract

The invention provides an eccentricity measuring device and method. The eccentricity measuring device is used for measuring the radial eccentricity of a radial transmission rod test piece of an engine under a test machine dynamic load. The eccentricity measuring device comprises a base, a rotating arm, a mounting structure, an identification piece and a sensor. Wherein the rotating arm is rotationally arranged on the base, and a test machine dynamic load acting on a radial transmission rod test piece is provided in the rotating process of the rotating arm; the mounting structure is arranged on the rotating arm; the radial transmission rod test piece is fixedly arranged on the mounting structure; the identification piece is arranged on the radial transmission rod test piece. The sensor is used for measuring the radial displacement of the identification piece. The eccentricity measuring device can improve the measuring precision.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of turbine engine, in particular to an eccentricity measuring device and method. BACKGROUND

[0002] The radial drive rod is a device for transmitting the motion and load between the high-pressure rotor and the gear box in the transmission system of a turbine engine. Under various operating conditions of the engine, the radial drive rod may be subjected to a dynamic load as high as 9g, which may cause the radial drive rod to deviate from the original axial position and produce deflection. Therefore, the eccentricity of the radial drive rod in the radial direction under the action of the dynamic load needs to be measured to evaluate the influence of the eccentricity on the spline wear.

[0003] It is difficult and costly to measure the eccentricity of the radial drive rod under the operating state of the engine. Moreover, the radial drive rod is a rotating member, and the test scheme involves a slip ring adapter, which is complex to modify. Therefore, a suitable test bench is usually required to simulate the load conditions.

[0004] However, if the offset distance of the spline connection of the radial drive rod is directly measured, the sensor cannot directly measure the offset of the measured part due to the complex structure and space problems. Moreover, since there is a tooth side gap between the inner and outer splines and a radial play in the bearing, the gap will be eliminated under the action of the dynamic load, which will be reflected in the offset of the spline, resulting in a large measurement error. SUMMARY

[0005] The purpose of the present application is to provide an eccentricity measuring device and method, which can reduce the error in calculating the eccentricity of the radial drive rod.

[0006] In one aspect, the present application provides an eccentricity measuring device for measuring the radial eccentricity of a radial drive rod test piece of an engine under a test dynamic load. The eccentricity measuring device comprises a base, a rotating arm, a mounting structure, a marker, and a sensor. The rotating arm is rotatably arranged on the base. The mounting structure is arranged on the rotating arm. The radial drive rod test piece is fixedly arranged on the mounting structure, and the rotating process of the rotating arm provides the test dynamic load acting on the radial drive rod test piece. The marker is arranged on the radial drive rod test piece, and the sensor is used to measure the radial displacement of the marker.

[0007] In one embodiment, the mounting structure is operatively movably arranged on the rotating arm in a non-test state to adjust the direction of the test dynamic load acting on the radial drive rod test piece.

[0008] In an embodiment, the radial drive bar test piece comprises a drive bar portion and a support portion; wherein the drive bar portion comprises a first drive bar; the support portion comprises a central transmission gearbox, the central transmission gearbox comprises a central transmission gearbox ball bearing, a central transmission gearbox bevel gear and a central transmission gearbox housing; a first spline end of the first drive bar and an inner spline of the central transmission gearbox bevel gear are in transmission connection; the central transmission gearbox ball bearing connects the central transmission gearbox bevel gear and the central transmission gearbox housing to support the central transmission gearbox housing; the identification member comprises a first identification block, a second identification block and a third identification block; the first identification block is arranged on an outer wall of one end of the central transmission gearbox housing close to the first spline end of the first drive bar, the second identification block is arranged on an outer wall of one end of the central transmission gearbox bevel gear provided with the inner spline, and the third identification block is arranged on an outer wall of the first spline end of the first drive bar; the sensor is used to measure the radial displacement of the first identification block, the second identification block and the third identification block respectively.

[0009] In an embodiment, the drive bar portion further comprises a second drive bar; the support portion further comprises an intermediate auxiliary bearing and an intermediate auxiliary housing; a first spline end of the second drive bar and a second spline end of the first drive bar are in transmission connection; the intermediate auxiliary bearing connects the first drive bar and the intermediate auxiliary housing to support the intermediate auxiliary housing; the identification member further comprises a fourth identification block, a fifth identification block and a sixth identification block; the fourth identification block is arranged on an outer wall of one end of the intermediate auxiliary housing close to the second spline end of the first drive bar, the fifth identification block is arranged on an outer wall of the second spline end of the first drive bar, and the sixth identification block is arranged on an outer wall of the first spline end of the second drive bar; the sensor is used to measure the radial displacement of the fourth identification block, the fifth identification block and the sixth identification block respectively.

[0010] In an embodiment, the supporting part further comprises a transfer gear box, the transfer gear box comprising a transfer gear box ball bearing, a transfer gear box bevel gear and a transfer gear box housing; the second spline end of the second transmission rod and the outer spline of the transfer gear box bevel gear are in transmission connection; the transfer gear box ball bearing connects the second spline end of the second transmission rod and the transfer gear box housing to support the transfer gear box housing; the identification part further comprises a seventh identification block, an eighth identification block and a ninth identification block; the seventh identification block is arranged on the outer wall of the second spline end of the second transmission rod, the eighth identification block is arranged on the outer wall of one end of the transfer gear box bevel gear provided with the outer spline, and the ninth identification block is arranged on the outer wall of one end of the transfer gear box housing close to the second spline end of the second transmission rod; the sensor is used to measure the radial displacement of the seventh identification block, the eighth identification block and the ninth identification block respectively.

[0011] Another aspect of the present application provides a eccentricity measurement method applied to the eccentricity measurement device as described in the above embodiments, the eccentricity measurement method comprising: obtaining the radial displacement of the identification part under different test machine dynamic loads; obtaining the corresponding relationship between the test machine dynamic load and the radial displacement of the radial transmission rod test piece according to the test machine dynamic load and the corresponding radial displacement of the identification part; determining the actual radial displacement of the first transmission rod and the second transmission rod in the radial transmission rod test piece according to the actual machine dynamic load and the corresponding relationship, and further obtaining the actual eccentricity of the first transmission rod and the second transmission rod.

[0012] In an embodiment, the obtaining the radial displacement of the radial transmission rod test piece under different test machine dynamic loads comprises: obtaining the second radial displacement of the second identification block and the third radial displacement of the third identification block under different test machine dynamic loads; the obtaining the corresponding relationship between the test machine dynamic load and the radial displacement of the radial transmission rod test piece according to the test machine dynamic load and the corresponding radial displacement of the identification part comprises: obtaining the second corresponding relationship between the test machine dynamic load and the first spline end of the first transmission rod according to the test machine dynamic load and the corresponding second radial displacement and third radial displacement.

[0013] In an embodiment, the obtaining the radial displacement of the radial transmission rod test piece under different test machine dynamic loads further comprises: obtaining fourth radial displacements of the fourth marker blocks and fifth radial displacements of the fifth marker blocks under different test machine dynamic loads; and the obtaining the corresponding relationship between the test machine dynamic loads and the radial displacements of the radial transmission rod test piece according to the test machine dynamic loads and the radial displacements of the corresponding marker blocks further comprises: obtaining a third corresponding relationship between the test machine dynamic loads and the radial displacements of the second spline end of the first transmission rod according to the test machine dynamic loads and the corresponding fourth radial displacements and fifth radial displacements.

[0014] In an embodiment, the obtaining the radial displacement of the radial transmission rod test piece under different test machine dynamic loads further comprises: obtaining sixth radial displacements of the sixth marker blocks under different test machine dynamic loads; and the obtaining the corresponding relationship between the test machine dynamic loads and the radial displacements of the radial transmission rod test piece according to the test machine dynamic loads and the radial displacements of the corresponding marker blocks further comprises: obtaining a fourth corresponding relationship between the test machine dynamic loads and the radial displacements of the first spline end of the second transmission rod according to the test machine dynamic loads and the corresponding fifth radial displacements and sixth radial displacements.

[0015] In an embodiment, the obtaining the radial displacement of the radial transmission rod test piece under different test machine dynamic loads further comprises: obtaining seventh radial displacements of the seventh marker blocks and eighth radial displacements of the eighth marker blocks under different test machine dynamic loads; and the obtaining the corresponding relationship between the test machine dynamic loads and the radial displacements of the radial transmission rod test piece according to the test machine dynamic loads and the radial displacements of the corresponding marker blocks further comprises: obtaining a sixth corresponding relationship between the test machine dynamic loads and the radial displacements of the second spline end of the second transmission rod according to the test machine dynamic loads and the corresponding seventh radial displacements and eighth radial displacements.

[0016] In an embodiment, the method for measuring the eccentricity of the central transmission gear box bevel gear comprises the following steps: obtaining the radial displacement of the radial transmission rod test piece under different test motor loads; obtaining the corresponding relationship between the test motor load and the radial displacement of the radial transmission rod test piece according to the test motor load and the radial displacement of the corresponding identification piece; and determining the actual radial displacement of the first transmission rod and the second transmission rod in the radial transmission rod test piece according to the actual motor load and the corresponding relationship, and then obtaining the actual eccentricity of the first transmission rod and the second transmission rod.

[0017]

[0018] wherein α1 is the actual eccentricity of the first transmission rod, α2 is the actual eccentricity of the second transmission rod, Δ 11 is the first actual radial displacement, Δ 12 is the second actual radial displacement, Δ 21 is the third actual radial displacement, Δ 22 is the fourth actual radial displacement, L1 is the length of the first transmission rod, and L2 is the length of the second transmission rod.

[0019] In an embodiment, the method for measuring the eccentricity of the central transmission gear box bevel gear comprises the following steps: obtaining the radial displacement of the radial transmission rod test piece under different test motor loads; obtaining the corresponding relationship between the test motor load and the radial displacement of the radial transmission rod test piece according to the test motor load and the radial displacement of the corresponding identification piece; and determining the actual radial displacement of the first transmission rod and the second transmission rod in the radial transmission rod test piece according to the actual motor load and the corresponding relationship, and then obtaining the actual eccentricity of the first transmission rod and the second transmission rod.

[0020] In an embodiment, the obtaining the radial displacement of the radial transmission rod test piece under different test machine dynamic loads further comprises: obtaining a ninth radial displacement of the ninth identification block under different test machine dynamic loads; the obtaining the corresponding relationship between the test machine dynamic load and the radial displacement of the radial transmission rod test piece according to the test machine dynamic load and the radial displacement of the corresponding identification piece further comprises: obtaining a fifth corresponding relationship between the test machine dynamic load and the radial displacement of the adapter gear box bevel gear according to the test machine dynamic load and the eighth radial displacement and the ninth radial displacement; the eccentricity measurement method further comprises: obtaining the actual radial displacement of the external spline of the adapter gear box bevel gear according to the actual machine dynamic load and the fifth corresponding relationship.

[0021] The eccentricity measurement device of the present application can solve the problem that the contact sensor cannot directly measure the measured part due to the compact space, and can eliminate the influence of the tooth side gap of the spline connection and the bearing play, so as to obtain the eccentricity value of the radial transmission rod caused by the dynamic load, thereby reducing the measurement error. BRIEF DESCRIPTION OF DRAWINGS

[0022] The above and other features, properties, and advantages of the present application will become more apparent by referring to the following description in conjunction with the accompanying drawings, in which:

[0023] Figure 1 is a schematic diagram of an embodiment of the eccentricity measurement device according to the present application;

[0024] Figure 2 is Figure 1 is a schematic diagram of the assembly state of the eccentricity measurement device and the radial transmission rod test piece in

[0025] Figure 3 is a schematic diagram of the radial transmission rod test piece and the identification block according to the present application;

[0026] Figure 4 is a flowchart of an embodiment of the eccentricity measurement method according to the present application. DETAILED DESCRIPTION

[0027] Reference will now be made in detail to embodiments of the invention, one or more examples of which are illustrated in the accompanying drawings. Each example is provided to explain the invention and not to limit it. In fact, it will be apparent to those skilled in the art that various modifications and variations may be made to the invention without departing from the scope or spirit thereof. For example, a feature shown or described as part of one embodiment may be used with another embodiment to produce yet another embodiment. Therefore, the invention is intended to cover these modifications and variations that fall within the scope of the appended claims and their equivalents.

[0028] As used herein, the term "axial" refers to the central axis of the radial drive shaft or the direction parallel to its central axis; the term "radial" refers to the direction perpendicular to the "axial" direction; and the term "circumferential" refers to the direction about the "axial" direction. The radial drive shaft is a component in a turbine engine used to transfer kinetic energy from the central drive gearbox to the transfer gearbox. It is also used to transmit starter torque to rotate the engine's high-pressure rotor, thereby starting the engine. The terms "first" through "ninth" are used interchangeably to distinguish one component from another and are not intended to indicate the location or importance of any component.

[0029] Figure 1 An embodiment of the eccentricity measuring device of the present invention is shown. The eccentricity measuring device of the present invention is used to measure the radial eccentricity of a radial drive rod test piece of an engine under test maneuver loads, that is, the radial eccentricity of the radial drive rod under maneuver loads simulating engine operation. Eccentricity is the angle of deviation between the actual axis of the drive rod and its theoretical axis due to the force applied to the drive rod. Radial displacement and offset are both deviation distances. Maneuver load is the load acting on the aircraft body during maneuvering flight.

[0030] like Figure 1 As shown, the eccentricity measuring device includes a base 100, a rotating arm 101, and a mounting structure 102. The base 100 is fixed to the ground or a test bench, serving as the foundation for the rotating centrifuge.

[0031] The rotating arm 101 is rotatably mounted on the base 100. The rotation of the rotating arm 101 provides the test kinetic load acting on the radial transmission rod test piece. The test kinetic load is achieved by the centrifugal acceleration generated by the rotation of the rotating arm 101. The rotating arm 101 can be driven by a DC motor (not shown). Control commands are transmitted to a DC speed controller via a host control computer or a touch screen (not shown) to control the rotation of the rotating arm 101, which is connected to the DC motor through a reducer and coupling, thus providing the load environment required for the test of the radial transmission rod test piece.

[0032] Figure 2 The radial transmission rod test piece 300 is shown assembled to the mounting structure 102. The radial transmission rod test piece 300 can be assembled to the mounting structure 102. Considering the large centrifugal force generated by the rotation of the rotating arm 101 during the test, the radial transmission rod test piece 300 needs to be fixedly arranged on the mounting structure 102 during assembly to ensure that the radial transmission rod test piece 300 does not displace relative to the mounting structure 102 during the rotation of the rotating arm 101, so as to ensure the consistency of the test machine dynamic load during the test. The mounting structure 102 is arranged at one end of the rotating arm 101 and is far away from the base 100. It can be understood that the centrifugal acceleration value generated by the rotation of the rotating arm 101 is the product of the length D of the rotating arm and the square of the angular velocity of the rotating arm 101. Among them, the length D of the rotating arm is the distance from the center of rotation of the base 100 to the center of the mounting structure 102. The greater the distance, the greater the centrifugal acceleration. The dynamic load is simulated by the centrifugal acceleration. This kind of measurement environment does not need real engine dynamic flight, and the radial transmission rod also does not need to work, and the whole eccentricity measurement device is simple and easy to operate.

[0033] In an embodiment, the mounting structure 102 is movably arranged on the rotating arm 101. In a non-test state, the mounting structure 102 can be operatively moved relative to the rotating arm 101 to adjust the direction of the test dynamic load acting on the radial transmission rod test piece 300. By changing the position of the mounting structure 102 relative to the base 100 and the rotating arm 101, the direction of the test dynamic load applied to the radial transmission rod test piece can be arbitrarily adjusted, which can reduce the workload.

[0034] As shown in Figure 2 , the mounting structure 102 includes a rack 102a and a mounting table 102b arranged on the rack 102a, and the radial transmission rod test piece 300 can be mounted on the mounting table 102b. In one embodiment, the rack 102a can rotate around the rotating shaft A on the rotating arm 101. In another embodiment, the mounting table 102b can be arranged on the rack 102a in any position. In yet another embodiment, the rack 102a can rotate around the rotating shaft A on the rotating arm 101, and the mounting table 102b can be arranged on the rack 102a in any position. Referring to Figure 2 , the axial direction of the radial transmission rod test piece 300 is perpendicular to the paper in the current state. By adjusting the rack 102a and / or the mounting table 102b, the axial direction of the radial transmission rod test piece 300 can be adjusted to any direction in space. By adjusting the relative position of the rack 102a and the rotating arm 101 and / or the relative position of the mounting table 102b and the rotating arm 101, the measurement of the eccentricity of the radial transmission rod test piece 300 under different direction test dynamic load conditions can be carried out.

[0035] The radial transmission rod test piece 300 can be fixedly installed on the installation table 102b through connecting bolts and positioning pins, and then the installation table 102b is fixedly installed above the rack 102a.

[0036] Figure 3 The structure of the radial transmission rod test piece 300 is shown. The eccentricity measuring device further comprises a marker 330 and a sensor (not shown). The marker 330 is arranged on the radial transmission rod test piece 300, and the sensor is used to measure the radial displacement of the marker 330.

[0037] As shown in Figure 2 , the installation structure 102 is provided with a fixed support 210, and the sensor is arranged on the fixed support 210. The sensor is opposite to the radial transmission rod test piece 300, and further, the sensor is opposite to the marker 330 on the radial transmission rod test piece 300. The sensor can be a contact type displacement sensor.

[0038] Due to the spatial layout of the turbine engine, the radial transmission rod is usually divided into two sections of hollow rods with large length-diameter ratio, i.e. an inner transmission rod and an outer transmission rod. The inner and outer transmission rods are both provided with floating splines at both ends. One end of the inner transmission rod is connected with a central transmission gear box at the high-pressure rotor end, one end of the outer transmission rod is connected with a transfer gear box, and an intermediate auxiliary bearing is designed between the inner and outer transmission rods, which has three supporting points.

[0039] Under the action of the motor load, the inner and outer rods of the radial transmission rod will produce a displacement in the radial direction of the transmission rod, so that the transmission rod generates an eccentricity, which will change the meshing state of the splines and bring an unbalanced load of the transmission rod. Therefore, the size of the eccentricity needs to be measured, and the vibration level of the inner and outer transmission rods, the working condition of the spline pair and how to reshape the splines according to the working condition need to be evaluated.

[0040] As shown in Figure 3 , according to the structure of the real engine radial transmission rod, the radial transmission rod test piece 300 of the eccentricity measuring device of the present application comprises a transmission rod part and a supporting part. The transmission rod part comprises a first transmission rod 321 (i.e. an inner transmission rod) and a second transmission rod 322 (i.e. an outer transmission rod). The supporting part comprises a central transmission gear box, an intermediate auxiliary bearing 307, an intermediate auxiliary bearing housing 308 and a transfer gear box. The central transmission gear box comprises a central transmission gear box ball bearing 309, a central transmission gear box bevel gear 311 and a central transmission gear box housing 312. The transfer gear box comprises a transfer gear box ball bearing 301, a transfer gear box bevel gear 303 and a transfer gear box housing 302.

[0041] As shown in Figure 3When the transmission system composed of the transmission rod part and the supporting part shown in the figure is in operation, the rotating speed and torque outputted by the central transmission gear box are transmitted to the adapter gear box through the first transmission rod 321 and the second transmission rod 322, the adapter gear box bevel gear 303 is connected with the second transmission rod 322, the second transmission rod 322 is connected with the first transmission rod 321, and the first transmission rod 321 is connected with the central transmission gear box bevel gear 311 through the spline.

[0042] With reference to the foregoing Figure 3 , in particular, the first spline end 310 of the first transmission rod 321 is in transmission connection with the inner spline of the central transmission gear box bevel gear 311. The first spline end 310 can be understood as the end of the first transmission rod 321 provided with the outer spline. The central transmission gear box ball bearing 309 connects the central transmission gear box bevel gear 311 and the central transmission gear box casing 312 to support the central transmission gear box casing 312.

[0043] The first spline end 306 of the second transmission rod 322 is in transmission connection with the second spline end 305 of the first transmission rod 321. The second spline end 305 can be understood as the end of the first transmission rod 321 provided with the inner spline; and the first spline end 306 can be understood as the end of the second transmission rod 322 provided with the outer spline. The intermediate auxiliary bearing 307 connects the first transmission rod 321 and the intermediate auxiliary casing 308 to support the intermediate auxiliary casing 308.

[0044] The second spline end 304 of the second transmission rod 322 is in transmission connection with the outer spline of the adapter gear box bevel gear 303. The second spline end 304 can be understood as the end of the second transmission rod 322 provided with the inner spline. The adapter gear box ball bearing 301 connects the second spline end 304 of the second transmission rod 322 and the adapter gear box casing 302 to support the adapter gear box casing.

[0045] The adapter gear box bevel gear 303 is supported by the adapter gear box ball bearing 301, and the load of the adapter gear box ball bearing 301 is transmitted to the external casing (not shown) through the adapter gear box casing 302. The first transmission rod 321 and the second transmission rod 322 are supported by the intermediate auxiliary bearing 307, and the load of the intermediate auxiliary bearing 307 is transmitted to the external casing through the intermediate auxiliary casing 308. The central transmission gear box bevel gear 311 is supported by the central transmission gear box ball bearing 309, and the load of the central transmission gear box ball bearing 309 is transmitted to the external casing through the central transmission gear box casing 312.

[0046] The eccentricity measuring device of the application uses a real engine radial transmission rod and a real supporting structure, and the installation platform 102b is designed to have a rigidity simulating the rigidity of a real fulcrum position, so that the hardware is changed less, the test data are real and reliable, and the device is easy to implement.

[0047] The identification component 330 includes a first identification block 339, a second identification block 338, a third identification block 337, a fourth identification block 336, a fifth identification block 335, a sixth identification block 334, a seventh identification block 333, an eighth identification block 332, and a ninth identification block 331.

[0048] The first marker block 339 is disposed on the outer wall of the central transmission gearbox housing 312, and is located at one end of the central transmission gearbox housing 312 near the first spline end 310 of the first transmission rod 321. The sensor can obtain the radial displacement d of the central transmission gearbox housing 312 by measuring the first radial displacement d1 of the first marker block 339. 11 .Right now:

[0049] d1=d 11 (1)

[0050] The second marking block 338 is disposed on the outer wall of the bevel gear 311 of the central transmission gearbox, near the end of the bevel gear 311 where the internal spline is provided. Because the ball bearing 309 of the central transmission gearbox has radial clearance, the second radial displacement d2 of the second marking block 338 measured by the sensor includes the radial displacement d of the central transmission gearbox housing 312. 11 Radial clearance d of ball bearing 309 in central drive gearbox 12 and the radial displacement d of the bevel gear 311 in the central transmission gearbox 13 .Right now:

[0051] d2=d 11 +d 12 +d 13 (2)

[0052] The third identification block 337 is disposed on the outer wall of the first spline end 310 of the first transmission rod 321. For example... Figure 3 As shown, due to space constraints, the third marker block 337 is positioned close to the second marker block 338. Because there is a tooth flank clearance between the internal spline of the central transmission gearbox bevel gear 311 and the first spline end 310 of the first transmission rod 321, the third radial displacement d3 of the third marker block 337, measured by the sensor, includes the radial displacement d of the central transmission gearbox housing 312. 11 Radial clearance d of ball bearing 309 in central drive gearbox 12 The radial displacement d of the bevel gear 311 in the central transmission gearbox 13 The radial displacement d of the first spline end 310 of the first transmission rod 321 14 and the tooth backlash d between the first spline end 310 of the first transmission rod 321 and the internal spline of the bevel gear 311 of the central transmission gearbox. 15 .Right now:

[0053] d3 = d 11 + d 12 + d 13 + d 14 + d 15 (3)

[0054] The fourth identification block 336 is disposed on the outer wall of the intermediate auxiliary housing 308, and is located at one end of the intermediate auxiliary housing 308 close to the second spline end of the first transmission rod 321 and the first spline end 306 of the second transmission rod 322. The sensor can obtain the radial displacement d 21 of the intermediate auxiliary housing 308 by measuring the fourth radial displacement d4 of the fourth identification block 336. That is:

[0055] d4 = d 21 (4)

[0056] The fifth identification block 335 is disposed on the outer wall of the second spline end 305 of the first transmission rod 321. Due to the radial clearance of the intermediate auxiliary bearing 307, the fifth radial displacement d5 of the fifth identification block 335 measured by the sensor includes the radial displacement d 21 of the intermediate auxiliary housing 308, the radial clearance d 22 of the intermediate auxiliary bearing 307, and the radial displacement d 23 of the second spline end 305 of the first transmission rod 321. That is:

[0057] d5 = d 21 + d 22 + d 23 (5)

[0058] The sixth identification block 334 is disposed on the outer wall of the first spline end 306 of the second transmission rod 322. As Figure 3 shown, due to space limitations, the sixth identification block 334 is disposed close to the fifth identification block 335. Due to the backlash between the first spline end 306 of the second transmission rod 322 and the second spline end 305 of the first transmission rod 321, the sixth radial displacement d6 of the sixth identification block 334 measured by the sensor includes the radial displacement d 21 of the intermediate auxiliary housing 308, the radial clearance d 22 of the intermediate auxiliary bearing 307, the radial displacement d 23 of the second spline end 305 of the first transmission rod 321, the radial displacement d 24 of the first spline end 306 of the second transmission rod 322, and the backlash d 25 between the second spline end 305 of the first transmission rod 321 and the first spline end 306 of the second transmission rod 322. That is:

[0059] d6 = d 21 + d22 +d 23 +d 24 +d 25 (6)

[0060] The seventh identification block 333 is arranged on the outer wall of the second spline end 304 of the second transmission rod 322. Since there is a tooth side gap between the outer spline of the adapter gearbox bevel gear 303 and the second spline end 304 of the second transmission rod 322, the seventh radial displacement d7 of the seventh identification block 333 measured by the sensor includes the radial displacement d 31 of the adapter gearbox housing 302, the radial play d 32 of the adapter gearbox ball bearing 301, the radial displacement d 33 of the adapter gearbox bevel gear 303, the radial displacement d 34 of the second spline end 304 of the second transmission rod 322, and the tooth side gap d 35 between the outer spline of the adapter gearbox bevel gear 303 and the second spline end 304 of the second transmission rod 322. That is:

[0061] d7 = d 31 +d 32 +d 33 +d 34 +d 35 (7)

[0062] The eighth identification block 332 is arranged on the outer wall of the adapter gearbox bevel gear 303 and located at one end of the outer spline of the adapter gearbox bevel gear 303. As shown in Figure 3 , due to space limitations, the eighth identification block 332 is arranged between the adapter gearbox housing 302 and the second spline end 304 of the second transmission rod 322. Since there is a radial play in the adapter gearbox ball bearing 301, the eighth radial displacement d8 of the eighth identification block 332 measured by the sensor includes the radial displacement d 31 of the adapter gearbox housing 302, the radial play d 32 of the adapter gearbox ball bearing 301, and the radial displacement d 33 of the adapter gearbox bevel gear 303. That is:

[0063] d8 = d 31 +d 32 +d 33 (8)

[0064] The ninth identification block 331 is arranged on the outer wall of the adapter gearbox housing 302 and located at one end close to the outer spline of the adapter gearbox bevel gear 303. The sensor can obtain the radial displacement d 31 of the adapter gearbox housing 302 by measuring the ninth radial displacement d9 of the ninth identification block 331. That is:

[0065] d9=d 31 (9)

[0066] According to the above relations (1) to (9), the sensors measure the radial displacements of the first identification block 339, the second identification block 338, the third identification block 337, the fourth identification block 336, the fifth identification block 335, the sixth identification block 334, the seventh identification block 333, the eighth identification block 332, and the ninth identification block 331, respectively, to obtain the corresponding nine radial displacements.

[0067] The tooth side gap is the gap or interval between the spline and the spline groove of the spline pair; the radial play is the movement amount of one of the inner ring or the outer ring of the ball bearing from one extreme position to the other extreme position, that is, the movement amount of the ball.

[0068] Using the sensors to measure the radial displacements of the identification blocks can solve the problem that the part space is compact and the contact type sensor cannot directly measure the measured part; at the same time, when the test machine dynamic load direction changes, the angles of the identification blocks can solve the problem of large cylindrical surface measurement error in some directions.

[0069] The eccentricity measurement method of the application is applied to an eccentricity measurement device as shown in Figures 1 to 3 As shown in Figure 4 The eccentricity measurement method includes steps S100 to S300:

[0070] In step S100, the radial displacement of the radial transmission rod test piece 300 under different test machine dynamic loads is obtained. Different test machine dynamic loads can be understood as different directions and different sizes of test machine dynamic loads.

[0071] In step S200, the corresponding relationship between the test machine dynamic load and the radial displacement of the radial transmission rod test piece 300 is obtained according to the test machine dynamic load and the radial displacement of the corresponding identification piece 330. The corresponding relationship is the influence law of the test machine dynamic load on the radial displacement of the radial transmission rod test piece 300.

[0072] In step S300, the actual radial displacements of the first transmission rod 321 and the second transmission rod 322 in the radial transmission rod test piece 300 are determined according to the actual machine dynamic load and the corresponding relationship, and the actual eccentricity of the first transmission rod 321 and the second transmission rod 322 is obtained.

[0073] The eccentricity measurement method of the application uses centrifugal acceleration to simulate the eccentricity measurement device of the machine dynamic load, eliminates the influence of the tooth side gap and the bearing play through the indirect measurement method, and further obtains the eccentricity of the first transmission rod 321 and the second transmission rod 322 caused by the actual machine dynamic load.

[0074] In one embodiment, step S100 further includes step S110:

[0075] In step S110, the first radial displacement d1 of the first marker block 339, the second radial displacement d2 of the second marker block 338, and the third radial displacement d3 of the third marker block 337 are obtained under different test motor loads.

[0076] According to the above relations (1) and (2), step S200 further includes steps S211 to S214:

[0077] In step S211, the first radial displacement d1 is subtracted from the second radial displacement d2 to obtain the radial clearance d of the ball bearing 309 in the central transmission gearbox. 12 Radial displacement d of bevel gear 311 in the central transmission gearbox 13 The sum of these is used as the first offset (d) 12 +d 13 ).

[0078] In step S212, the test maneuver load is increased until it reaches the first target test maneuver load to eliminate the first offset (d). 12 +d 13 radial clearance d in ) 12 The impact.

[0079] In step S213, based on the test maneuver load greater than the first target test maneuver load and the corresponding first offset (d) 12 +d 13 ), thus obtaining the first correspondence f1.

[0080] Analysis of experimental data shows that as the centrifugal acceleration increases (0–3g), the radial clearance d of the ball bearing 309 in the central transmission gearbox increases. 12 The centrifugal acceleration of the first target test load is eliminated, i.e., 3g. When the centrifugal acceleration increases further (3g~10g), it enters the linear stage of centrifugal deformation, from which the radial displacement d of the load on the bevel gear 311 of the central transmission gearbox can be obtained. 13 The influence pattern, namely the first correspondence f1.

[0081] In step S214, the actual radial displacement of the internal spline of the bevel gear 311 of the central transmission gearbox is obtained based on the actual motor load and the first correspondence f1.

[0082] Through the above steps S211 to S214, the relative position between the internal spline of the central transmission gearbox bevel gear 311, which is a spline pair, and the first spline end 310 of the first transmission rod 321 can be determined, thereby analyzing the working condition of the spline pair and preventing jamming and spline wear.

[0083] In an embodiment, according to the above-mentioned relationship (2) and (3), the step S200 further comprises steps S221-S223:

[0084] In step S221, the third radial displacement d3 is subtracted from the second radial displacement d2 to obtain the radial displacement d 14 of the first spline end 310 of the first transmission rod 321. 15 The sum of the tooth side clearance d 14 and the tooth side clearance d 15 between the first spline end 310 of the first transmission rod 321 and the inner spline of the central transmission gear box bevel gear 311 is taken as the second offset (d 14 +d 15 ).

[0085] In step S222, the test machine dynamic load is increased to the second target test machine dynamic load to eliminate the influence of the tooth side clearance d 15 in the second offset (d 14 +d 15 ).

[0086] In step S223, the second corresponding relationship f2 is obtained according to the test machine dynamic load greater than the second target test machine dynamic load and the corresponding second offset (d 14 +d 15 ).

[0087] Through analysis of the test data, it can be known that, with the increase of the centrifugal acceleration (0-5g), the tooth side clearance d 15 is eliminated, i.e. the centrifugal acceleration of the second target test machine dynamic load is 5g. When the centrifugal acceleration is further increased (5g-10g), it is in the linear stage of the centrifugal deformation, and thus the influence law of the test machine dynamic load on the radial displacement d 14 of the first spline end 310 of the first transmission rod 321 can be obtained, i.e. the second corresponding relationship f2.

[0088] In an embodiment, the step S100 further comprises step S120:

[0089] In step S120, the fourth radial displacement d4 of the fourth identification block 336, the fifth radial displacement d5 of the fifth identification block 335 and the sixth radial displacement d6 of the sixth identification block 334 under different test machine dynamic loads are obtained.

[0090] According to the above-mentioned relationship (4) and (5), the step S200 further comprises steps S231-S233:

[0091] In step S231, the fifth radial displacement d5 is subtracted from the fourth radial displacement d4 to obtain the radial play d 22The radial displacement d of the second spline end 305 of the first transmission rod 321 23 The sum of these is used as the third offset (d) 22 +d 23 ).

[0092] In step S232, the test maneuver load is increased until it reaches the third target test maneuver load to eliminate the third offset (d). 22 +d 23 radial clearance d in ) 22 The impact.

[0093] In step S233, based on the test maneuver load greater than the target test maneuver load and the corresponding third offset (d) 22 +d 23 ), thus obtaining the third correspondence f3.

[0094] Analysis of experimental data shows that as the centrifugal acceleration increases (0–3g), the radial clearance d of the intermediate auxiliary bearing 307 increases. 22 The centrifugal acceleration of the third target test motor load is 3g, which is eliminated. When the centrifugal acceleration increases further (3g to 10g), it is the linear stage of centrifugal deformation. From this, the influence law of the motor load on the radial displacement of the second spline end 305 of the first transmission rod 321 can be obtained, namely the third correspondence f3.

[0095] According to the above relations (5) and (6), step S200 further includes steps S241 to S243:

[0096] In step S241, the fifth radial displacement d5 is subtracted from the sixth radial displacement d6 to obtain the radial displacement d of the first spline end 306 of the second transmission rod 322. 24 The tooth flank clearance d between the first spline end 306 of the second transmission rod 322 and the second spline end 305 of the first transmission rod 321 25 The sum of these is used as the fourth offset (d) 24 +d 25 ).

[0097] In step S242, the test maneuver load is increased until it reaches the fourth target test maneuver load to eliminate the fourth offset (d). 24 +d 25 Tooth flank clearance d in ) 25 The impact.

[0098] In step S243, based on the test maneuver load greater than the fourth target test maneuver load and the corresponding fourth offset (d) 24 +d 25 ), thus obtaining the fourth correspondence f4.

[0099] According to the analysis of the test data, with the increase of the centrifugal acceleration (0~5g), the radial clearance d 25 is eliminated, i.e. the centrifugal acceleration of the fourth target test motor load is 5g. When the centrifugal acceleration is further increased (5g~10g), it is the linear stage of the centrifugal deformation, and thus the influence law of the motor load on the radial displacement of the first spline end 306 of the second transmission rod 322, i.e. the fourth corresponding relationship f4, can be obtained.

[0100] In an embodiment, the step S100 further includes a step S130:

[0101] In the step S130, the seventh radial displacement d7 of the seventh identification block 333, the eighth radial displacement d8 of the eighth identification block 332 and the ninth radial displacement d9 of the ninth identification block 331 under different test motor loads are obtained.

[0102] According to the above relationships (8) and (9), the step S200 further includes steps S251 to S254:

[0103] In the step S251, the eighth radial displacement d8 is subtracted by the ninth radial displacement d9 to obtain the radial displacement d 33 of the adapter gear box bevel gear 303, which is the sum of the radial clearance d 32 of the adapter gear box ball bearing 301 and the fifth offset amount (d 32 +d 33 ).

[0104] In the step S252, the test motor load is increased to the fifth target test motor load to eliminate the influence of the radial clearance d 32 of the adapter gear box ball bearing 301 in the fifth offset amount (d 33 +d 32 ).

[0105] In the step S253, according to the test motor load greater than the fifth target test motor load and the corresponding fifth offset amount (d 32 +d 33 ), the fifth corresponding relationship f5 is obtained.

[0106] According to the analysis of the test data, with the increase of the centrifugal acceleration (0~3g), the radial clearance d 32 of the adapter gear box ball bearing 301 is eliminated, i.e. the centrifugal acceleration of the fifth target test motor load is 3g. When the centrifugal acceleration is further increased (3g~10g), it is the linear stage of the centrifugal deformation, and thus the influence law of the motor load on the radial displacement d 33 of the adapter gear box bevel gear 303, i.e. the fifth corresponding relationship f5, can be obtained.

[0107] In step S254, the actual radial displacement of the external spline of the adapter gear box bevel gear is obtained according to the actual maneuvering load and the fifth corresponding relationship f5.

[0108] Through the above steps S251 to S254, the relative position between the external spline of the adapter gear box bevel gear 303 and the second spline end 304 of the second driving rod 322 as a spline pair is determined, and the working condition of the spline pair is analyzed to prevent the spline from being worn out due to jamming.

[0109] In an embodiment, according to the above relationships (7) and (8), step S200 further includes steps S261 to S263:

[0110] In step S261, the seventh radial displacement d7 is subtracted from the eighth radial displacement d8 to obtain the radial displacement d 34 of the second spline end 304 of the second driving rod 322. The sum of the backlash d 35 of the second spline end 304 of the second driving rod 322 and the external spline of the adapter gear box bevel gear 303 is taken as the sixth offset (d 34 +d 35 ).

[0111] In step S262, the test maneuvering load is increased to a sixth target test maneuvering load to eliminate the influence of the backlash d 34 of the sixth offset (d 35 +d 35 ).

[0112] In step S263, the sixth corresponding relationship f6 is obtained according to the test maneuvering load greater than the sixth target test maneuvering load and the corresponding sixth offset (d 34 +d 35 ).

[0113] Through analysis of the test data, it is found that as the centrifugal acceleration increases (0-5g), the backlash d 35 is eliminated, i.e., the centrifugal acceleration of the sixth target test maneuvering load is 5g. When the centrifugal acceleration further increases (5g-10g), it is in the linear stage of the centrifugal deformation, and thus the influence of the maneuvering load on the radial displacement d 34 of the second spline end 304 of the second driving rod 322 can be obtained, i.e., the sixth corresponding relationship f6.

[0114] It should be noted that the order of steps S110, S120 and S130 is not limited. The order of steps S211 to S214, S221 to S223, S231 to S233, S241 to S243, S251 to S254 and S261 to S263 is not limited.

[0115] On the basis of the above-mentioned embodiments, step S300 further comprises steps S310-S320:

[0116] In step S310, a first actual radial displacement of the first spline end 310 of the first transmission rod 321 is determined according to the actual motor load and the second corresponding relationship f2; a second actual radial displacement of the second spline end 305 of the first transmission rod 321 is determined according to the actual motor load and the third corresponding relationship f3; a third actual radial displacement of the first spline end 306 of the second transmission rod 322 is determined according to the actual motor load and the fourth corresponding relationship f4; and a fourth actual radial displacement of the second spline end 304 of the second transmission rod 322 is determined according to the actual motor load and the sixth corresponding relationship f6.

[0117] In step S320, the actual eccentricity of the first transmission rod 321 and the second transmission rod 322 is obtained according to the following relationship:

[0118]

[0119] Wherein, α1 is the actual eccentricity of the first transmission rod 321, α2 is the actual eccentricity of the second transmission rod 322, Δ 11 is the first actual radial displacement, Δ 12 is the second actual radial displacement, Δ 21 is the third actual radial displacement, Δ 22 is the fourth actual radial displacement, L1 is the length of the first transmission rod 321, and L2 is the length of the second transmission rod 322.

[0120] If the directions of Δ 11 and Δ 12 are opposite, the signs of the two are opposite; similarly, if the directions of Δ 21 and Δ 22 are opposite, the signs of the two are opposite.

[0121] By respectively measuring the displacement of each part when the centrifugal acceleration of the test motor load increases by 1g in the interval [0, 10g], the influence law of the motor load on the eccentricity of the first transmission rod 321 and the second transmission rod 322 is indirectly obtained, and the problem of large measurement error caused by the existence of the backlash and bearing clearance is solved.

[0122] Although the present application is disclosed with the preferred embodiments as above, it is not intended to limit the present application, and any person skilled in the art can make possible changes and modifications without departing from the spirit and scope of the present application. Therefore, any modification, equivalent change and modification made to the above embodiments according to the technical essence of the present application, which does not deviate from the technical solutions of the present application, falls within the protection scope defined by the claims of the present application.

Claims

1. An eccentricity measuring device for measuring the radial eccentricity of a radial drive bar test piece of an engine under a dynamic load of a testing machine, characterized by, The eccentricity measuring device comprises a base, a rotating arm, a mounting structure, a marker and a sensor, wherein The rotating arm is arranged on the base in a rotating manner; The mounting structure is arranged on the rotating arm; The radial transmission rod test piece is fixedly arranged on the mounting structure, and the rotating process of the rotating arm provides the test machine dynamic load acting on the radial transmission rod test piece; The marker is arranged on the radial transmission rod test piece, and the sensor is used for measuring the radial displacement of the marker.

2. The eccentricity measuring device of claim 1, wherein The mounting structure is arranged on the rotating arm in an operable manner in a non-test state to adjust the direction of the test machine dynamic load acting on the radial transmission rod test piece.

3. The eccentricity measuring device of claim 2, wherein The radial transmission rod test piece comprises a transmission rod part and a supporting part, wherein The transmission rod part comprises a first transmission rod; The supporting part comprises a central transmission gear box, the central transmission gear box comprises a central transmission gear box ball bearing, a central transmission gear box bevel gear and a central transmission gear box machine case; The first spline end of the first transmission rod and the inner spline of the central transmission gear box bevel gear are in transmission connection; The central transmission gear box ball bearing connects the central transmission gear box bevel gear and the central transmission gear box machine case to support the central transmission gear box machine case; The marker comprises a first marker block, a second marker block and a third marker block; The first marker block is arranged on the outer wall of one end of the central transmission gear box machine case close to the first spline end of the first transmission rod, the second marker block is arranged on the outer wall of one end of the central transmission gear box bevel gear provided with the inner spline, and the third marker block is arranged on the outer wall of the first transmission rod close to the first spline end; The sensor is used for measuring the radial displacement of the first marker block, the second marker block and the third marker block respectively.

4. The eccentricity measuring device of claim 3, wherein The transmission rod part further comprises a second transmission rod; The supporting part further comprises an intermediate auxiliary bearing and an intermediate auxiliary machine case; The first spline end of the second transmission rod and the second spline end of the first transmission rod are in transmission connection; The intermediate auxiliary bearing connects the first transmission rod and the intermediate auxiliary machine case to support the intermediate auxiliary machine case; The marker further comprises a fourth marker block, a fifth marker block and a sixth marker block; The fourth marker block is arranged on the outer wall of one end of the intermediate auxiliary machine case close to the second spline end of the first transmission rod, the fifth marker block is arranged on the outer wall of the second spline end of the first transmission rod, and the sixth marker block is arranged on the outer wall of the first spline end of the second transmission rod; The sensor is used for measuring the radial displacement of the fourth marker block, the fifth marker block and the sixth marker block respectively.

5. The eccentricity measuring device of claim 4, wherein The supporting part further comprises a switching gear box, the switching gear box comprises a switching gear box ball bearing, a switching gear box bevel gear and a switching gear box machine case; The second spline end of the second transmission rod and the outer spline of the switching gear box bevel gear are in transmission connection; The adapter gear box ball bearing connects the second spline end of the second transmission rod and the adapter gear box housing to support the adapter gear box housing; The identification member further comprises a seventh identification block, an eighth identification block and a ninth identification block; The seventh identification block is arranged on the outer wall of the second spline end of the second transmission rod, the eighth identification block is arranged on the outer wall of the end of the adapter gear box bevel gear provided with the external spline, and the ninth identification block is arranged on the outer wall of the end of the adapter gear box housing close to the second spline end of the second transmission rod; The sensor is used to measure the radial displacement of the seventh identification block, the eighth identification block and the ninth identification block respectively.

6. An eccentricity measuring method applied to the eccentricity measuring device according to claim 5, characterized in that, The eccentricity measurement method comprises: Obtaining the radial displacement of the identification member under different test machine dynamic loads; According to the test machine dynamic load and the corresponding radial displacement of the identification member, a corresponding relationship between the test machine dynamic load and the radial displacement of the radial transmission rod test piece is obtained; According to the actual machine dynamic load and the corresponding relationship, the actual radial displacement of the first transmission rod and the second transmission rod in the radial transmission rod test piece is determined, and then the actual eccentricity of the first transmission rod and the second transmission rod is obtained.

7. The eccentricity measurement method of claim 6, wherein The obtaining of the radial displacement of the radial transmission rod test piece under different test machine dynamic loads comprises: Obtaining the second radial displacement of the second identification block and the third radial displacement of the third identification block under different test machine dynamic loads; The corresponding relationship between the test machine dynamic load and the radial displacement of the radial transmission rod test piece is obtained according to the test machine dynamic load and the corresponding radial displacement of the identification member, which comprises: According to the test machine dynamic load and the corresponding second radial displacement and third radial displacement, a second corresponding relationship between the test machine dynamic load and the second spline end of the first transmission rod is obtained.

8. The eccentricity measurement method of claim 7, wherein, The obtaining of the radial displacement of the radial transmission rod test piece under different test machine dynamic loads further comprises: Obtaining the fourth radial displacement of the fourth identification block and the fifth radial displacement of the fifth identification block under different test machine dynamic loads; The corresponding relationship between the test machine dynamic load and the radial displacement of the radial transmission rod test piece is obtained according to the test machine dynamic load and the corresponding radial displacement of the identification member, which further comprises: According to the test machine dynamic load and the corresponding fourth radial displacement and fifth radial displacement, a third corresponding relationship between the test machine dynamic load and the radial displacement of the second spline end of the first transmission rod is obtained.

9. The eccentricity measurement method of claim 8, wherein, The obtaining of the radial displacement of the radial transmission rod test piece under different test machine dynamic loads further comprises: Obtaining the sixth radial displacement of the sixth identification block under different test machine dynamic loads; The corresponding relationship between the test machine dynamic load and the radial displacement of the radial transmission rod test piece is obtained according to the test machine dynamic load and the corresponding radial displacement of the identification member, which further comprises: According to the test motor load and the corresponding seventh radial displacement and the eighth radial displacement, a sixth corresponding relationship between the test motor load and the second spline end of the second transmission rod is obtained.

10. The eccentricity measurement method of claim 9, wherein, The obtaining of the radial displacement of the radial transmission rod test piece under different test motor loads further includes: Obtaining a seventh radial displacement of the seventh identification block and an eighth radial displacement of the eighth identification block under different test motor loads; The corresponding relationship between the test motor load and the radial displacement of the radial transmission rod test piece according to the test motor load and the corresponding radial displacement of the identification piece further includes: According to the test motor load and the corresponding seventh radial displacement and the eighth radial displacement, a sixth corresponding relationship between the test motor load and the second spline end of the second transmission rod is obtained.

11. The eccentricity measurement method of claim 10, wherein, The actual radial displacement of the first transmission rod and the second transmission rod in the radial transmission rod test piece is determined according to the actual motor load and the corresponding relationship, and the actual eccentricity of the first transmission rod and the second transmission rod is obtained, including: According to the actual motor load and the second corresponding relationship, the first actual radial displacement of the first spline end of the first transmission rod is determined, according to the actual motor load and the third corresponding relationship, the second actual radial displacement of the second spline end of the first transmission rod is determined, according to the actual motor load and the fourth corresponding relationship, the third actual radial displacement of the first spline end of the second transmission rod is determined, and according to the actual motor load and the sixth corresponding relationship, the fourth actual radial displacement of the second spline end of the second transmission rod is determined; The actual eccentricity of the first transmission rod and the second transmission rod is obtained according to the following relationship: wherein a1 is the actual eccentricity of the first transmission rod, a2 is the actual eccentricity of the second transmission rod, Δ 11 is the first actual radial displacement, 12 is the second actual radial displacement, 21 is the third actual radial displacement, 22 is the fourth actual radial displacement, L1 is the length of the first transmission rod, and L2 is the length of the second transmission rod.

12. The eccentricity measurement method according to any one of claims 7 to 11, wherein The obtaining of the radial displacement of the radial transmission rod test piece under different test motor loads further includes: Obtaining a first radial displacement of the first identification block under different test motor loads; The corresponding relationship between the test motor load and the radial displacement of the radial transmission rod test piece according to the test motor load and the corresponding radial displacement of the identification piece further includes: According to the test motor load and the corresponding first radial displacement and the second radial displacement, a first corresponding relationship between the test motor load and the radial displacement of the central transmission gear box bevel gear is obtained; The eccentricity measurement method further includes: According to the actual motor load and the first corresponding relationship, the actual radial displacement of the inner spline of the central transmission gear box bevel gear is obtained.

13. The eccentricity measurement method according to claim 10 or 11, wherein The obtaining of the radial displacement of the radial transmission rod test piece under different test motor loads further includes: Obtaining a ninth radial displacement of the ninth identification block under different test motor loads; The corresponding relationship between the test motor load and the radial displacement of the radial transmission rod test piece according to the test motor load and the corresponding radial displacement of the identification piece further includes: According to the test motor load and the corresponding eighth radial displacement and the ninth radial displacement, a fifth corresponding relationship between the test motor load and the radial displacement of the taper gear of the adapter gear box is obtained; The eccentricity measurement method further includes: According to the actual motor load and the fifth corresponding relationship, the actual radial displacement of the external spline of the taper gear of the adapter gear box is obtained.

Images