A dynamic balancing testing device and a testing method thereof

Abstract

The application provides a dynamic balance testing device and a testing method thereof, and belongs to the technical field of dynamic balance testing, wherein the device comprises a spiral bevel gear assembly and a dynamic balance machine, and the spiral bevel gear assembly is clamped on the dynamic balance machine. The spiral bevel gear assembly of the application can improve the bearing capacity and cooling effect of the spiral bevel gear assembly of the main reducer, and meet the use requirements of an aero-engine. By arranging the ball bearing, the cylindrical roller bearing and the bearing seat, the radial bearing capacity of the ball bearing is low, the gap fit provides axial support for the gear shaft, the radial bearing capacity of the cylindrical roller bearing is high, and the axial bearing capacity is low. By arranging the two different bearings, the high radial bearing capacity and the high axial bearing capacity can be realized, the wear of the bearing is reduced, and the operation life of the bearing is improved.

Description

Technical Field

[0001] The present invention belongs to the technical field of dynamic balance testing, and in particular relates to a dynamic balance testing device and a testing method thereof. Background Art

[0002] In the prior art, there are two main ways to perform dynamic balancing: adding weight and reducing weight. That is, first use a dynamic balancing machine to measure the imbalance, and then determine the weight that needs to be added or reduced at the corresponding position based on the imbalance to achieve the final balanced state. For the high-speed spiral bevel gear assembly of the aircraft reducer, its operating speed is usually above 20,000 rpm, and the vibration caused by the imbalance is very harmful to the reducer. However, since the high-speed bevel gear assembly of the aircraft reducer is provided with components that require high cleanliness, if the high-speed bevel gear assembly of the aircraft reducer is dynamically balanced using the methods of adding weight and reducing weight as a whole, foreign matter such as cutting debris may be introduced, resulting in a reduction in service life and damage to the overall mechanical properties. In the prior art, after ensuring that the components of the high-speed bevel gear assembly of the aircraft reducer meet the dynamic balancing requirements, the high-speed bevel gear assembly of the aircraft reducer is marked and assembled, and it is believed that the assembled high-speed bevel gear assembly of the aircraft reducer meets the use requirements.

[0003] Since the existing technology only considers the dynamic balance of individual components, it does not take into account that the overall assembly after assembly may become unbalanced due to combination and installation factors. The overall dynamic balance accuracy is low, which cannot meet the actual working needs of the helicopter aviation reducer and may also cause failures in the use of the aviation reducer high-speed bevel gear assembly; in addition, the main reducer spiral bevel gear assembly in the existing technology has insufficient load-bearing capacity and poor cooling effect. Summary of the Invention

[0004] In response to the above problems, a dynamic balancing test device and a test method thereof are provided.

[0005] In order to achieve the above object, the present invention adopts the following technical solutions:

[0006] A dynamic balancing test device comprises a spiral bevel gear assembly and a dynamic balancing machine, wherein the spiral bevel gear assembly is clamped on the dynamic balancing machine;

[0007] The spiral bevel gear assembly includes a first bearing inner ring, a gear shaft, a second bearing, a third bearing and a bearing seat;

[0008] The first bearing inner ring is coaxially arranged with the gear shaft and has an interference fit;

[0009] The second bearing and the third bearing are coaxially mounted on the gear shaft;

[0010] The second bearing is connected to the third bearing along the axial direction of the gear shaft;

[0011] The bearing seat is arranged on the outer ring of the second bearing and the third bearing;

[0012] The bearing seat is interference fit with the second bearing;

[0013] The bearing seat is clearance fit with the third bearing;

[0014] The gear shaft surface is provided with a transmission groove.

[0015] Preferably, the gear shaft is provided with a second nut at one end close to the inner ring of the first bearing, and one end surface of the second nut is abutted with one end surface of the inner ring of the first bearing;

[0016] An opening is arranged on the end surface of the second nut away from the inner ring of the first bearing, a groove is arranged on the inner wall of the opening, a spiral retainer is arranged in the groove, and a stop washer is arranged between the spiral retainer and the bottom surface of the opening.

[0017] Preferably, the gear shaft is a hollow shaft, and a plurality of first oil channels are arranged in the radial direction;

[0018] The inner ring of the second bearing is provided with a plurality of second oil channels for guiding the lubricating oil of the first oil channels into the second bearing;

[0019] The inner ring of the third bearing is provided with a plurality of third oil channels for guiding the lubricating oil of the first oil channels into the third bearing;

[0020] The bearing seat is internally provided with a fourth oil channel for guiding the lubricating oil of the second bearing and the third bearing out of the oil return pipeline.

[0021] Preferably, the second bearing is a cylindrical roller bearing, and the third bearing is a ball bearing;

[0022] The end surface of the outer ring of the second bearing is provided with a plurality of connecting grooves;

[0023] The end surface of the outer ring of the third bearing is provided with a plurality of lugs;

[0024] The lugs are embedded in the connecting grooves.

[0025] Preferably, the gear shaft is provided with a flange at one end away from the inner ring of the first bearing;

[0026] The end surface of the flange away from the inner ring of the first bearing is abutted with a first nut, and the first nut is threadedly connected with the gear shaft;

[0027] One end of the flange away from the first nut is sleeved on the gear shaft;

[0028] A spline is arranged between the inner surface of the flange and the outer surface of the gear shaft.

[0029] Preferably, the end surface of the flange plate abuts against a mechanical seal, which is located in the gap between the bearing seat and the gear shaft.

[0030] The mechanical seal is located away from one end of the flange plate and abuts against the third bearing.

[0031] Preferably, a plurality of fastening bolts are installed at one end of the flange plate away from the gear shaft, and a flat washer is arranged between the fastening bolts and the flange plate.

[0032] Preferably, the dynamic balancing machine comprises a movable assembly, a fixed assembly and a motor, and a belt is installed between the output shaft of the motor and the transmission groove.

[0033] The motor is located between the movable assembly and the fixed assembly.

[0034] The movable assembly is used for fixing the inner ring of the first bearing.

[0035] The fixed assembly is used for fixing the bearing seat.

[0036] A testing method of a dynamic balancing testing device, comprising the following steps:

[0037] A dynamic balancing finite element analysis model of the bevel gear assembly is constructed.

[0038] The assembly position affecting the unbalance is determined based on the dynamic balancing finite element analysis model.

[0039] The dynamic balancing calibration of the bevel gear assembly is performed based on the assembly position.

[0040] Preferably, the dynamic balancing calibration of the bevel gear assembly based on the assembly position comprises the following steps:

[0041] The motor is started, the gear shaft is driven to the target rotating speed through the belt, and the unbalance of the bevel gear assembly is measured after the rotation is uniform and the number is stable.

[0042] If the unbalance is greater than 20g / mm, the spiral retainer and / or the flange plate are rotated, the relative installation angle of the spiral retainer and the gear shaft is adjusted, and / or the first nut is loosened, the relative installation angle of the flange plate and the gear shaft is adjusted, and the first nut is tightened.

[0043] The dynamic balancing test is performed again until the maximum residual unbalance of the bevel gear assembly is not more than 20g / mm.

[0044] The beneficial effects of the present application are as follows:

[0045] 1. The spiral bevel gear assembly can improve the bearing capacity and cooling effect of the main reducer spiral bevel gear assembly, and meet the use requirements of the aero-engine.

[0046] 2、The ball bearing, cylindrical roller bearing and bearing seat are arranged, the radial bearing capacity of the ball bearing is low, the gap fit provides axial support for the gear shaft, the radial bearing capacity of the cylindrical roller bearing is high and the axial bearing capacity is low, the high radial bearing capacity and high axial bearing capacity are realized by arranging the two different bearings, the wear of the bearing is reduced, and the running life of the bearing is improved;

[0047] 3、The dynamic balance testing method of the application does not adopt the weight or weight reduction method in the prior art, avoids affecting the operation of the overall structure, adjusts the relative installation angle of the spiral retaining ring, input gear shaft, input flange plate and input gear shaft, and realizes machining-free dynamic balance;

[0048] 4、The application reduces the overall unbalance of the bevel gear assembly, meets the actual needs, improves the operation stability and safety of the high-speed bevel gear assembly of the aviation speed reducer, quickly reduces the unbalance through the combination of finite element analysis and physical testing, realizes machining-free dynamic balance by adjusting the relative installation angle of the spiral retaining ring, input gear shaft, input flange plate and input gear shaft, and improves the bearing capacity of the bearing through the cooperation of the two bearings.

[0049] Other features and advantages of the present application will be set forth in the following description, and in part will become apparent to those skilled in the art from the description, or can be learned by practice of the present application. The objects and other advantages of the present application can be achieved and obtained by the structure indicated in the description and drawings. BRIEF DESCRIPTION OF DRAWINGS

[0050] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the following will briefly introduce the drawings needed to be used in the embodiments or the prior art description. Obviously, the drawings in the following description are some embodiments of the present application, and those skilled in the art can obtain other drawings according to these drawings without creative labor.

[0051] Figure 1 A schematic view of a spiral bevel gear assembly structure of the present application is shown;

[0052] Figure 2 An enlarged view of the A area in Figure 1 is shown;

[0053] Figure 3 An enlarged view of the B area in Figure 1 is shown;

[0054] Figure 4The structural diagram of a dynamic balance testing device of a spiral bevel gear assembly of the present application is shown.

[0055] In the figure: 1, first bearing inner ring; 2, gear shaft; 201, transmission groove; 202, first oil path; 203, annular groove; 3, second bearing; 301, second oil path; 302, connecting groove; 4, third bearing; 401, third oil path; 402, convex jaw; 5, mechanical seal; 6, bearing seat; 601, fourth oil path; 7, flange plate; 8, spline; 9, first nut; 10, fastening bolt; 11, flat washer; 12, second nut; 13, spiral retainer; 14, stop washer; 15, adjusting frame; 1501, lower roller support; 1502, roller; 1503, upper roller support; 16, fixing frame; 1601, positioning support; 17, belt; 18, motor. DETAILED DESCRIPTION

[0056] To make the objectives, technical solutions and advantages of the embodiments of the present application clearer, the technical solutions in the embodiments of the present application will be described clearly and completely below with reference to the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are some but not all of the embodiments of the present application. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative work fall within the protection scope of the present application.

[0057] A dynamic balance testing device comprises a spiral bevel gear assembly and a dynamic balancing machine, the spiral bevel gear assembly is clamped on the dynamic balancing machine, as shown in Figure 1 the spiral bevel gear assembly comprises a first bearing inner ring 1, a gear shaft 2, a second bearing 3, a third bearing 4 and a bearing seat 6, wherein the first bearing inner ring 1 is arranged at one end of the gear shaft 2 and is in interference fit with the gear shaft 2, the second bearing 3 and the third bearing 4 are coaxially installed on the gear shaft 2, the second bearing 3 is connected with the third bearing 4 along the gear shaft 2 in the axial direction, the bearing seat 6 is arranged on the outer ring of the second bearing 3 and the third bearing 4, the bearing seat 6 is in interference fit with the second bearing 3, and the bearing seat 6 is in clearance fit with the third bearing 4, and the clearance is generally 0.5 mm, the gear shaft 2 is provided with a transmission groove 201 on the surface, and the transmission groove 201 is arranged between the first bearing inner ring 1 and the second bearing 3.

[0058] It should be noted that, in Figure 1 the spiral bevel gear assembly is a rotary body structure, in addition, the interference fit between the second bearing 3 and the bearing seat 6 is used to make the second bearing 3 bear the radial force and be basically not subjected to the axial force; conversely, the clearance fit between the third bearing 4 and the bearing seat 6 is used to bear the axial force and be basically not subjected to the radial force; therefore, the second bearing 3 and the third bearing 4 can guarantee that the assembly can bear larger pressure in the radial direction and the axial direction and is not easy to be damaged.

[0059] Furthermore, if Figure 2 As shown, a second nut 12 is installed at one end of the gear shaft 2 close to the first bearing inner ring 1, and one end face of the second nut 12 is abutted against one end face of the first bearing inner ring 1. An opening is provided on the end face of the second nut 12 away from the first bearing inner ring 1, and a groove is provided on the inner wall of the opening. A spiral retaining ring 13 is installed in the groove, and a stop washer 14 is provided between the spiral retaining ring 13 and the bottom surface of the opening; the second nut 12 is used to fix the first bearing inner ring 1, and the function of the stop washer 14 is to prevent the second nut 12 from loosening, and the spiral retaining ring 13 further presses the stop washer 14.

[0060] Furthermore, the gear shaft 2 is a hollow shaft and has several first oil passages 202 opened in the radial direction. The inner ring of the second bearing 3 has several second oil passages 301 opened, and the second oil passages 301 are used to introduce the lubricating oil of the first oil passage 202 into the second bearing 3. The inner ring of the third bearing 4 has several third oil passages 401 opened, and the third oil passages 401 are used to introduce the lubricating oil of the first oil passage 202 into the third bearing 4. In addition, a fourth oil passage 601 is opened inside the bearing seat 6, and the fourth oil passage 601 is used to guide the lubricating oil of the second bearing 3 and the third bearing 4 to the return oil pipeline.

[0061] It should be noted that, from Figure 1 It can be seen that the fourth oil passage 601 first opens an oil passage along the axial direction of the bearing seat 6, and then opens an oil passage along the radial direction. The lubricating oil entering the first oil passage 202 first reaches the inner ring position of the second bearing 3 and the third bearing 4, and then gradually penetrates into the outer ring. Since the fourth oil passage 601 is opened near the outer ring, the lubricating oil enters the fourth oil passage 601 and finally enters the return oil pipeline, thereby achieving sufficient lubrication and cooling of the second bearing 3 and the third bearing 4.

[0062] It needs to be further explained that Figure 1 As can be seen, multiple first oil passages 202 are provided, as are multiple second oil passages 301, located at both ends of the inner ring. Multiple third oil passages 401 are provided, located in the middle of the inner ring, corresponding to the first oil passages 202. Furthermore, annular grooves 203 are provided at the tops of the two right-side first oil passages 202. One of these annular grooves 203 is located at the junction of the second bearing 3 and the third bearing 4, allowing cooling oil from the second oil passage 301 to enter the second bearing 3 and the third bearing 4 through the gap at the junction. The other annular groove 203 corresponds to the position of the third oil passage 401.

[0063] Further, combined with Figure 1 and Figure 3 The second bearing 3 is a cylindrical roller bearing, the third bearing 4 is a ball bearing, the outer ring end surface of the second bearing 3 is provided with a plurality of connecting grooves 302, and the outer ring end surface of the third bearing 4 is provided with a plurality of cams 402, which are embedded in the connecting grooves 302.

[0064] It should be noted that the cylindrical roller bearing can bear large radial force, while the ball bearing can bear large axial force, and the structure of the lugs 402 and the connecting grooves 302 is used to connect the second bearing 3 and the third bearing 4 together, and the outer rings of the two bearings cannot rotate relative to each other. It should be noted that the setting of the annular groove 203 can ensure the communication with the oil passage hole of the gear shaft 2 when the inner rings of the cylindrical roller bearing and the ball bearing are sleeved on the gear shaft 2 at any angle, thereby improving the reliability of the oil passage communication and reducing the difficulty of component installation.

[0065] Further, a flange plate 7 is installed at the end of the gear shaft 2 away from the first bearing inner ring 1, the end face of the flange plate 7 away from the first bearing inner ring 1 abuts against a first nut 9, the first nut 9 is threadedly connected with the gear shaft 2, the end of the flange plate 7 away from the first nut 9 is sleeved on the gear shaft 2, and a spline 8 is arranged between the inner surface of the flange plate 7 and the outer surface of the gear shaft 2. The end face of the flange plate 7 abuts against a mechanical seal 5, the mechanical seal 5 is located in the gap between the bearing seat 6 and the gear shaft 2, and the end of the mechanical seal 5 away from the flange plate 7 abuts against the third bearing 4.

[0066] Further, a plurality of fastening bolts 10 are installed at the end of the flange plate 7 away from the gear shaft 2, and a flat washer 11 is arranged between the fastening bolt 10 and the flange plate 7.

[0067] It should be noted that the fastening bolts 10 are arranged on the flange plate 7, one fastening bolt 10 (generally a twelve-angle bolt) and five flat washers 11 form a group of fastening members, and there are three groups in total, which are used to simulate the connection between the high-speed bevel gear assembly of the aviation speed reducer and other components.

[0068] As shown in Figure 4 , the dynamic balancing machine comprises a movable assembly, a fixed assembly, and a motor 18, a belt 17 is installed between the output shaft of the motor 18 and the transmission groove 201;

[0069] The motor 18 is located between the movable assembly and the fixed assembly;

[0070] The movable assembly is used to fix the first bearing inner ring 1;

[0071] The fixed assembly is used to fix the bearing seat 6.

[0072] It should be noted that the dynamic balancing machine further comprises a horizontal bottom plate, and the movable assembly, the fixed assembly, and the motor 18 can be installed on the bottom plate.

[0073] Among them, the movable assembly and the fixed assembly have various embodiments, and one of them will be introduced as follows:

[0074] As shown in Figure 4As shown, the active assembly includes an adjusting frame 15, a lower roller support 1501 and an upper roller support 1503, both of which are mounted on the adjusting frame 15, the lower roller support 1501 is provided with at least two rotatable rollers 1502, and the upper roller support 1503 is provided with at least one rotatable roller 1502, and the at least three rollers 1502 fix the first bearing inner ring 1.

[0075] It should be noted that the lower roller support 1501 and the upper roller support 1503 can be designed to slide relative to the adjusting frame 15, and then fixed after moving to the target position, so that the relative positions of the three rollers 1502 can be adjusted to clamp different specifications of the first bearing inner ring 1, for example, a plurality of through holes are formed on the lower roller support 1501 and the upper roller support 1503, and then at least two bolts are matched in the through holes, and finally the upper roller support 1503 and the lower roller support 1501 are fixed on the adjusting frame 15 through the bolts.

[0076] The fixed assembly includes a fixed frame 16 and a positioning support 1601, and the positioning support 1601 is mounted on the fixed frame 16, the fixed frame 16 is used to place the bearing seat 6, and the positioning support 1601 is used to abut against the bearing seat 6 along the radial direction of the bearing seat 6.

[0077] It should be noted that the same positioning support 1601 can also be designed as a sliding device relative to the fixed frame 16, and then fixed after sliding to the target position.

[0078] A dynamic balance testing method, comprising the following steps:

[0079] A dynamic balance finite element analysis model of the bevel gear assembly is constructed;

[0080] The assembly position affecting the unbalance is determined based on the dynamic balance finite element analysis model;

[0081] The bevel gear assembly is dynamically balanced based on the assembly position.

[0082] Further, the dynamic balance calibration of the bevel gear assembly based on the assembly position comprises the following steps:

[0083] Start the motor 18, drive the gear shaft 2 to the target speed through the belt 17, and measure the unbalance of the bevel gear assembly after rotating at a constant speed and stable number;

[0084] If the unbalance is greater than 20g / mm, rotate the spiral retainer 13 and / or the flange plate 7, adjust the relative installation angle of the spiral retainer 13 and the gear shaft 2, and / or loosen the first nut 9, adjust the relative installation angle of the flange plate 7 and the gear shaft 2, and tighten the first nut 9;

[0085] The dynamic balance test is performed again until the maximum residual unbalance of the bevel gear assembly is less than or equal to 20 g / mm.

[0086] An embodiment of a dynamic balance test method is provided as follows:

[0087] S1: constructing a dynamic balance finite element analysis model of the spiral bevel gear assembly of the main speed reducer of an aircraft, comprising:

[0088] S101: obtaining parameters of each part of the spiral bevel gear assembly of the main speed reducer, establishing a finite element model and assembling each part model;

[0089] S2: determining an assembly position affecting the unbalance based on the dynamic balance finite element analysis model, comprising:

[0090] S201: performing dynamic balance simulation of the finite element model, and from the simulation results of the dynamic balance finite element analysis model, it is known that the assembly positions of the flange plate 7 and the gear shaft 2 and the assembly positions of the spiral retainer 13 and the gear shaft 2 affect the unbalance of the bevel gear assembly;

[0091] S3: performing dynamic balance calibration of the bevel gear assembly based on the assembly position, comprising:

[0092] S301: installing three sets of fasteners, each set of fasteners including one fastening bolt 10 and five flat washers 11, weighing each set of fasteners, and requiring the weight difference between each set to be less than 0.025 g; installing the three sets of fasteners on the corresponding pallet nuts of the flange plate 7 of the bevel gear assembly, respectively, and fixing them firmly;

[0093] S302: adjusting the distance between the fixed assembly and the movable assembly, installing the spiral bevel gear assembly of the main speed reducer on the dynamic balance machine, adjusting the height of the fixed assembly and the movable assembly to keep the spiral bevel gear assembly of the main speed reducer in a horizontal state, and then fixing it firmly on the dynamic balance machine;

[0094] S303: connecting the belt 17 in the transmission groove 201 and tightening it, then closing the protective cover of the balance machine; starting the balance machine to slowly increase the speed to the target speed (2000-2020 rpm), rotating at a uniform speed, and measuring the unbalance of the high-speed bevel gear assembly of the aircraft speed reducer after the number is stable;

[0095] S304: analyzing the obtained unbalance, if the unbalance is greater than 20 g / mm, rotating the spiral retainer 13 and / or the flange plate 7 according to the analysis results, adjusting the relative installation angle of the spiral retainer 13 and the gear shaft 2, and / or loosening the first nut 9, adjusting the relative installation angle of the flange plate 7 and the gear shaft 2 and tightening the first nut 9, and performing the dynamic balance test again, so that the maximum residual unbalance of the bevel gear assembly is less than or equal to 20 g / mm;

[0096] S305: calibration ends, the aviation main reducer spiral bevel gear assembly is taken off from the dynamic balance testing device as a whole, and can be directly used for subsequent installation or testing.

[0097] Although the present application has been described in detail with reference to the foregoing embodiments, it should be understood that the technical solutions recorded in the foregoing embodiments can be modified, or some technical features can be replaced by equivalent features, by those skilled in the art, without departing from the spirit and scope of the technical solutions of the embodiments of the present application.

Claims

1. A dynamic balance test device, characterized in that: It includes a spiral bevel gear assembly and a dynamic balancing machine, wherein the spiral bevel gear assembly is clamped on the dynamic balancing machine; The spiral bevel gear assembly comprises a first bearing inner ring (1), a gear shaft (2), a second bearing (3), a third bearing (4) and a bearing seat (6); The first bearing inner ring (1) and the gear shaft (2) are coaxially arranged and have an interference fit; The second bearing (3) and the third bearing (4) are coaxially mounted on the gear shaft (2); The second bearing (3) is connected to the third bearing (4) along the axial direction of the gear shaft (2); The bearing seat (6) is arranged on the outer rings of the second bearing (3) and the third bearing (4); a second nut (12) is installed on one end of the gear shaft (2) close to the inner ring (1) of the first bearing, and one end face of the second nut (12) abuts against one end face of the inner ring (1) of the first bearing; An opening is provided on the end surface of the second nut (12) away from the first bearing inner ring (1), a groove is provided on the inner wall of the opening, a spiral retaining ring (13) is installed in the groove, and a stop washer (14) is provided between the spiral retaining ring (13) and the bottom surface of the opening; The bearing seat (6) and the second bearing (3) are interference fit; The bearing seat (6) and the third bearing (4) are clearance-fitted; A transmission groove (201) is provided on the surface of the gear shaft (2); the gear shaft (2) is a hollow shaft and has a plurality of first oil passages (202) provided radially. The inner ring of the second bearing (3) is provided with a plurality of second oil passages (301), and the second oil passages (301) are used to guide the lubricating oil in the first oil passage (202) into the second bearing (3); The inner ring of the third bearing (4) is provided with a plurality of third oil passages (401), and the third oil passages (401) are used to guide the lubricating oil of the first oil passage (202) into the third bearing (4); A fourth oil circuit (601) is provided inside the bearing seat (6), and the fourth oil circuit (601) is used to guide the lubricating oil of the second bearing (3) and the third bearing (4) to the oil return pipeline; A flange (7) is mounted on one end of the gear shaft (2) away from the first bearing inner ring (1); The end surface of the flange (7) away from the first bearing inner ring (1) is in contact with a first nut (9), and the first nut (9) is threadedly connected to the gear shaft (2); One end of the flange (7) away from the first nut (9) is sleeved on the gear shaft (2); A spline (8) is provided between the inner surface of the flange (7) and the outer surface of the gear shaft (2).

2. A dynamic balance test device according to claim 1, characterized in that: The second bearing (3) is a cylindrical roller bearing, and the third bearing (4) is a ball bearing; The outer ring end surface of the second bearing (3) is provided with a plurality of connecting grooves (302); The outer ring end surface of the third bearing (4) is provided with a plurality of protruding claws (402); The protruding claw (402) is embedded in the connecting groove (302).

3. A dynamic balance test device according to claim 1, characterized in that: The end surface of the flange (7) is in contact with a mechanical seal (5), and the mechanical seal (5) is located in the gap between the bearing seat (6) and the gear shaft (2); One end of the mechanical seal (5) away from the flange (7) abuts against the third bearing (4).

4. A dynamic balance test device according to claim 1, characterized in that: A plurality of fastening bolts (10) are installed on one end of the flange (7) away from the gear shaft (2), and a flat washer (11) is provided between the fastening bolts (10) and the flange (7).

5. A dynamic balance test device according to claim 4, characterized in that: The dynamic balancing machine includes a movable component, a fixed component, and a motor (18), wherein a belt (17) is installed between the output shaft of the motor (18) and the transmission groove (201); The motor (18) is located between the movable component and the fixed component; The movable assembly is used to fix the first bearing inner ring (1); The fixing assembly is used to fix the bearing seat (6).

6. The testing method of a dynamic balance testing device according to claim 5, characterized in that: The following steps are involved: Construct a dynamic balancing finite element analysis model for bevel gear assemblies; Determine the assembly position that affects the imbalance based on the dynamic balancing finite element analysis model; Dynamically balance bevel gear assemblies based on the assembly position.

7. The testing method of a dynamic balance testing device according to claim 6, characterized in that: The dynamic balancing calibration of the bevel gear assembly based on the assembly position includes the following steps: Start the motor (18), drive the gear shaft (2) to increase the speed to the target speed through the belt (17), and measure the unbalance of the bevel gear assembly after the rotation speed is uniform and the reading is stable; If the unbalance is greater than 20 g / mm, rotate the spiral retaining ring (13) and / or the flange (7), adjust the relative installation angle between the spiral retaining ring (13) and the gear shaft (2), and / or loosen the first nut (9), adjust the relative installation angle between the flange (7) and the gear shaft (2) and tighten the first nut (9); Perform the dynamic balancing test again until the maximum residual unbalance of the bevel gear assembly does not exceed 20g / mm.

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