A generator dynamic balancing test device

Abstract

This invention relates to the field of dynamic balancing testing technology, specifically to a generator dynamic balancing testing device. The generator dynamic balancing testing device is configured to perform dynamic balancing tests on the generator rotor. The device includes a test platform, a support assembly, a timing belt, and a pulley assembly. The support assembly is mounted on the test platform and configured to support the rotor's rotation. The timing belt is mounted on the test platform and forms a closed motion loop on it. The pulley assembly is mounted on the test platform and configured to enable the timing belt to form a closed motion loop. The timing belt has a fixed section that wraps around the top of the rotor during use and makes frictional contact with the rotor. Thus, when the rotor rotates, the fixed section provides external constraint to the rotor, ensuring the stable support conditions required for the dynamic balancing test and guaranteeing the accuracy of the test results.

Description

Technical Field

[0001] This invention relates to the field of dynamic balancing testing technology, and in particular to a generator dynamic balancing testing device. Background Technology

[0002] Dynamic balancing testing of a generator is an important step in ensuring that vibration and noise are minimized when it rotates at high speeds. By adjusting the mass distribution of the rotor, unbalanced forces can be eliminated or reduced, thereby improving the stability and service life of the generator.

[0003] When performing dynamic balancing tests on generator rotors, dynamic balancing testing equipment is required. Related technologies, such as Chinese patent application CN118882917A, disclose a rotor dynamic balancing testing mechanism. In this mechanism, the rotor is first placed on a belt. Since the belt is initially tensioned, it deforms under the weight of the rotor. The belt applies a force to the third driven pulley, which in turn moves the first slider on the slide rail. This changes the belt tension, allowing the belt to deform differently depending on the rotor's mass, thus avoiding the influence of insufficient belt tension on the test results.

[0004] However, the aforementioned rotor dynamic balancing test mechanism also has some problems in actual testing: the mechanism is essentially a combination of adaptive tension mechanical transmission mechanism and rotor free support state, but due to the lack of external constraints on rotor motion under vibration state, the stiffness of the support system will change dynamically with rotor vibration, which will destroy the stable support conditions required for dynamic balancing test and thus affect the test results. Summary of the Invention

[0005] Therefore, it is necessary to provide a generator dynamic balancing test device to address the problem of poor test results in the current rotor dynamic balancing test process.

[0006] The above objectives are achieved through the following technical solutions:

[0007] A generator dynamic balancing testing device is configured to perform dynamic balancing tests on the rotor of a generator; the generator dynamic balancing testing device includes:

[0008] Test platform;

[0009] A support assembly is disposed on the test platform and configured to support the rotation of the rotor;

[0010] A timing belt is provided on the test platform and forms a closed motion loop on the test platform. The timing belt has a fixed section, which wraps around the top of the rotor and makes frictional contact with the rotor during use.

[0011] A pulley assembly is disposed on the test platform and configured to enable the limiting timing belt to form a closed motion loop.

[0012] Furthermore, the pulley assembly includes a bracket on which a driving pulley, an elastic tensioning pulley, a first driven pulley, two second driven pulleys, and two active tensioning pulleys are rotatably mounted about their own axis. The driving pulley, the elastic tensioning pulley, the first driven pulley, and the two active tensioning pulleys are all located inside the limiting synchronous belt and are in frictional contact with the limiting synchronous belt. The two second driven pulleys are located outside the limiting synchronous belt and are in frictional contact with the limiting synchronous belt. The elastic tensioning pulley is configured to elastically tension the limiting synchronous belt. The two active tensioning pulleys are symmetrically arranged about the rotor.

[0013] Furthermore, the limiting synchronous belt is configured to have an acceleration state and a stable state. In the acceleration state, the limiting synchronous belt is configured to drive the rotor to rotate at an accelerated speed; in the stable state, the limiting synchronous belt is configured to drive the rotor to rotate at a constant speed; and in the acceleration state, the area of ​​the fixed section surrounding the rotor is greater than the area of ​​the fixed section surrounding the rotor in the stable state. The generator dynamic balancing test device also includes an adjustment mechanism, which is configured to adjust the state of the limiting synchronous belt.

[0014] Furthermore, the active tensioning wheel is capable of sliding in a vertical direction; the adjustment mechanism includes two third driven wheels and two driving members, both of which are mounted on the bracket and located inside the limiting synchronous belt, and are symmetrically arranged about the rotor; the driving members are mounted on the bracket and configured to provide a driving force for the active tensioning wheel to slide in a vertical direction; the active tensioning wheel has corresponding first and second positions before and after sliding; when in the first position, the limiting synchronous belt is in a first state, and the limiting synchronous belt is wound around the active wheel, the elastic tensioning wheel, the first driven wheel, the two second driven wheels, and the two active tensioning wheels; when in the second position, the limiting synchronous belt is in a second state, and the limiting synchronous belt is wound around the active wheel, the elastic tensioning wheel, the first driven wheel, the two second driven wheels, and the two third driven wheels.

[0015] Furthermore, the active tensioning pulley has a fixed and coaxially arranged first sub-pulley and two second sub-pulleys, with the two second sub-pulleys located on both sides of the first sub-pulley and having a diameter larger than the first sub-pulley; the third driven pulley has a fixed and coaxially arranged third sub-pulley and two fourth sub-pulleys, with the two fourth sub-pulleys located on both sides of the third sub-pulley and having a diameter smaller than the third sub-pulley; there are three limiting synchronous belts, which are arranged side by side, with the middle limiting synchronous belt configured to cooperate with either the first or third sub-pulley, and the limiting synchronous belts on both sides configured to cooperate with either the second or fourth sub-pulleys.

[0016] Furthermore, the diameter difference between the first and second pulleys is less than the thickness of the limiting synchronous belt; the diameter difference between the third and fourth pulleys is less than the thickness of the limiting synchronous belt.

[0017] Furthermore, the test platform is also provided with a first support, and the bracket is hinged to the first support; the generator dynamic balancing test device also includes a drive assembly, which is configured to provide a driving force for the rotation of the bracket.

[0018] Furthermore, the first support can slide in a direction parallel to the rotor axis.

[0019] Furthermore, the support assembly includes two second supports, which are arranged at intervals along a direction parallel to the rotor axis; each second support is provided with two rollers, the axis of the rollers is parallel to the rotor axis, and the rollers are rotatable around their own axis. The rollers on different second supports are correspondingly arranged, and the two rollers on the same second support are arranged along a direction perpendicular to the rotor axis and form a support area between them. The support area is configured to support the rotor.

[0020] Furthermore, both of the second supports are capable of sliding in a direction parallel to the rotor axis.

[0021] The beneficial effects of this invention are:

[0022] This invention relates to a generator dynamic balancing test device. By setting a limiting synchronous belt with a fixed section, the fixed section wraps around the top of the rotor during use and makes frictional contact with the rotor. This not only drives the rotor to rotate but also applies external constraints to the rotor, thereby ensuring the stable support conditions required for dynamic balancing tests and ensuring the accuracy of test results.

[0023] Furthermore, by setting the synchronous belt to have acceleration and steady states, in the acceleration state, the fixed section covers a larger area of ​​the rotor, resulting in a larger interaction force between the fixed section and the rotor, thus ensuring that the fixed section can stably drive the rotor to accelerate, which is beneficial to improving test efficiency. In the steady state, the fixed section covers a smaller area of ​​the rotor, resulting in a smaller interaction force between the fixed section and the rotor, which on the one hand ensures that the rotor can rotate stably, and on the other hand reduces the rotor vibration effect caused by the uneven thickness of the belt, which is beneficial to improving the accuracy of test results.

[0024] Furthermore, by setting the active tensioning wheel to have a fixed and coaxially arranged first sub-gear and two second sub-gears, with the diameter of the first sub-gear being smaller than the diameter of the second sub-gears, and by setting three limiting synchronous belts arranged side by side, when the limiting synchronous belts are in an accelerating state, the limiting synchronous belts on both sides have a greater tension and provide greater friction when in contact with the rotor, thereby ensuring the stability of the rotor during acceleration. By setting the third driven wheel to have a fixed and coaxially arranged third sub-gear and two fourth sub-gears, with the diameter of the third sub-gear being larger than the diameter of the fourth sub-gears, when the limiting synchronous belts are in a stable state, the limiting synchronous belt in the middle has a greater tension and provides greater friction when in contact with the rotor, thereby reducing the vibration impact of limiting synchronous belt wear on the rotor dynamic balance test.

[0025] Furthermore, by setting the diameter difference between the first and second pulleys to be less than the thickness of the limiting synchronous belt, and the diameter difference between the third and fourth pulleys to be less than the thickness of the limiting synchronous belt, the three limiting synchronous belts overlap in the thickness direction before and after the limiting synchronous belt switching state. This allows the three limiting synchronous belts to mutually limit each other, preventing polarization from affecting the rotor dynamic balance test. Attached Figure Description

[0026] Figure 1 This is a three-dimensional structural diagram of the generator dynamic balancing test device provided in an embodiment of the present invention;

[0027] Figure 2 This is a side view of the generator dynamic balancing test device provided in an embodiment of the present invention.

[0028] Figure 3 A three-dimensional structural diagram of the generator dynamic balancing test device provided in an embodiment of the present invention during dynamic balancing test of the rotor;

[0029] Figure 4 This is a side view of the generator dynamic balancing test device provided in an embodiment of the present invention during dynamic balancing testing of the rotor.

[0030] Figure 5This is a front view of the generator dynamic balancing test device provided in an embodiment of the present invention during dynamic balancing testing of the rotor.

[0031] Figure 6 for Figure 5 A three-dimensional sectional view along the AA direction;

[0032] Figure 7 for Figure 6 A magnified schematic diagram of the structure at point X in the middle;

[0033] Figure 8 This is a three-dimensional cross-sectional view of the generator dynamic balancing test device provided in an embodiment of the present invention during dynamic balancing testing of the rotor.

[0034] Figure 9 for Figure 8 A magnified schematic diagram of the structure at point Y in the middle;

[0035] Figure 10 A three-dimensional structural diagram of the third driven wheel of the generator dynamic balancing test device provided in an embodiment of the present invention;

[0036] Figure 11 This is a three-dimensional structural diagram of the generator dynamic balancing test device provided in an embodiment of the present invention, showing the assembly of the active tensioning wheel and the first drive cylinder.

[0037] in:

[0038] 1. Test platform; 101. Second slide rail;

[0039] 2. Support components; 201. Second support; 202. Rotary wheel;

[0040] 3. Limit the timing belt;

[0041] 401, bracket; 4011, first slide groove; 402, drive wheel; 403, elastic tension wheel; 4031, support rod; 4032, compression spring; 404, first driven wheel; 405, second driven wheel; 406, drive tension wheel; 4061, first sub-wheel; 4062, second sub-wheel; 407, first drive motor;

[0042] 501, Third driven wheel; 5011, Third sub-wheel; 5012, Fourth sub-wheel; 502, First drive cylinder;

[0043] 6. First support;

[0044] 7. Drive assembly; 701. Second drive motor; 702. Transmission belt; 703. Fixed pulley;

[0045] 8. Rotor. Detailed Implementation

[0046] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below through embodiments and in conjunction with the accompanying drawings. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.

[0047] The component designations used in this document, such as "first" and "second," are merely for distinguishing the described objects and do not have any sequential or technical meaning. The terms "connection" and "linkage," unless otherwise specified, include both direct and indirect connections (linkages). In the description of this invention, it should be understood that the terms "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," and "counterclockwise," indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings and are only for the convenience of describing the invention and simplifying the description. They do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as limiting the invention.

[0048] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0049] The following reference Figures 1 to 11 This invention describes a generator dynamic balancing test device provided in an embodiment of the invention. It is particularly suitable for dynamic balancing tests of generator rotor 8. Of course, it can also be applied to dynamic balancing tests of other shaft types, rotor types, and other components.

[0050] Specifically, the rotor 8 is installed with its axis extending horizontally in the left-right direction. The generator dynamic balancing test device is configured to include a test platform 1, a support assembly 2, a limiting synchronous belt 3, and a pulley assembly. The support assembly 2 is mounted on the test platform 1 and configured to support the rotation of the rotor 8. It can be configured to include two second supports 201, which are arranged horizontally at intervals in the left-right direction. Each second support 201 is hinged with two rollers 202. The two rollers 202 on the same second support 201 are arranged horizontally in the front-back direction. The axis of the rollers 202 is parallel to the axis of the rotor 8. The rollers 202 on different second supports 201 are correspondingly arranged to ensure that the rotor 8 can be supported along its axial direction.

[0051] The timing belt 3 is a ring structure and is set on the test platform 1, forming a closed motion loop on the test platform 1. The timing belt 3 is located above the rotor 8, ensuring that it can form an external constraint on the rotor 8 from top to bottom. The pulley assembly is set on the test platform 1 and configured to enable the timing belt 3 to form a closed motion loop. It can be configured to include a bracket 401 and a first drive motor 407. The bracket 401 is provided with a driving pulley 402, an elastic tensioning pulley 403, a first driven pulley 404, two second driven pulleys 405, and two driving tensioning pulleys 406, which are rotatable around their own axis. Figure 6 As shown, the elastic tensioning wheel 403 is located above and behind the driving wheel 402; the first driven wheel 404 and the elastic tensioning wheel 403 are at the same horizontal height, with the first driven wheel 404 located behind the elastic tensioning wheel 403; two second driven wheels 405 are at the same horizontal height and located between the driving wheel 402 and the first driven wheel 404, with one second driven wheel 405 located below and in front of the first driven wheel 404, and the other second driven wheel 405 located below and behind the elastic tensioning wheel 403; two driving tensioning wheels 406 are at the same horizontal height and are symmetrically arranged about the rotor 8, both located below the driving wheel 402, with one driving tensioning wheel 406 being the driving tensioning wheel 402. Wheel 406 is located below and in front of the second driven wheel 405, which is positioned at the rear. Another active tensioning wheel 406 is located below and behind the second driven wheel 405, which is positioned at the front. The active wheel 402, the elastic tensioning wheel 403, the first driven wheel 404, and the two active tensioning wheels 406 are all located inside the limiting synchronous belt 3 and are in frictional contact with the limiting synchronous belt 3. The two second driven wheels 405 are located outside the limiting synchronous belt 3 and are in frictional contact with the limiting synchronous belt 3. When the first drive motor 407 is installed, the motor shaft is coaxial and fixedly inserted into the axle of the active wheel 402 to ensure that it can drive the active wheel 402 to rotate, thereby making the limiting synchronous belt 3 form a closed motion circuit.

[0052] A support rod 4031 is also inserted into the bracket 401. The support rod 4031 extends horizontally in the front-to-back direction and is at the same horizontal height as the elastic tension wheel 403. The front end of the support rod 4031 is hinged to the axle of the elastic tension wheel 403, ensuring that the elastic tension wheel 403 can rotate freely. A compression spring 4032 is sleeved on the support rod 4031. The two ends of the compression spring 4032 abut against the bracket 401 and the elastic tension wheel 403, respectively. Under the action of the compression spring 4032, the support rod 4031 tends to drive the elastic tension wheel 403 forward, thereby elastically tensioning the timing belt 3. Optionally, to improve the stability of the elastic tension wheel 403 during movement, two support rods 4031 can be provided. The two support rods 4031 are symmetrically arranged about the elastic tension wheel 403, and each support rod 4031 is sleeved with a compression spring 4032.

[0053] In the field of dynamic balancing testing of generator rotor 8, the test mechanism based on adaptive tensioning of the limiting synchronous belt 3 achieves tension adjustment through mechanical transmission. Its core logic is to use the gravity of rotor 8 to induce deformation of limiting synchronous belt 3, and through the mechanical linkage between driven wheel and slider, the tension of limiting synchronous belt 3 is dynamically adapted to the mass of rotor 8. Although it solves the problem of mismatch between the preload of limiting synchronous belt 3 and the weight of rotor 8 in traditional fixed tensioning structures, its mechanical transmission mechanism and the motion state of rotor 8 are fundamentally contradictory in the scenario of unbalanced vibration of rotor 8.

[0054] From the perspective of mechanical transmission path, the existing testing mechanism places the rotor 8 entirely on the freely supported limiting synchronous belt 3. When the rotor 8 vibrates due to centrifugal force generated by uneven mass distribution, it will experience periodic radial displacement. At this time, the limiting synchronous belt 3 must not only bear the static gravity of the rotor 8 but also cope with the dynamic vibration load. Since the rotor 8 is in an unconstrained free state, the radial force generated by the vibration will directly act on the support surface of the limiting synchronous belt 3, causing the limiting synchronous belt 3 to undergo asymmetrical deformation. This deformation will drive the slider to reciprocate on the slide rail through the driven wheel, transforming the mechanical structure originally used for adaptive tension adjustment into a transmission path for vibration energy. The reciprocating motion of the slider not only changes the tension of the limiting synchronous belt 3 but also introduces additional mechanical disturbances.

[0055] From the perspective of system stability, dynamic balancing testing requires rotor 8 to maintain a relatively stable support state during rotation to ensure the accuracy of vibration signal acquisition. However, in existing testing mechanisms, the dynamic changes in the tension of the limiting synchronous belt 3 caused by rotor 8 vibration create a positive feedback effect of "vibration-tension change-vibration aggravation": when rotor 8 imbalance causes vibration, the tension of the limiting synchronous belt 3 changes due to the movement of the slider, and the change in support stiffness further alters the vibration characteristics of rotor 8, causing the originally singular imbalance vibration to be superimposed with parametric vibrations caused by changes in support stiffness. This complex vibration state causes the vibration signal of the testing system to contain interference components unrelated to the imbalance, making it difficult to accurately separate the characteristic frequencies corresponding to the imbalance during spectrum analysis, thus affecting the calculation accuracy of the dynamic balancing correction.

[0056] From the perspective of mechanical constraint principles, the lack of a limiting mechanism for the radial movement of rotor 8 in the free support structure is the fundamental reason for the deviation in test results. In dynamic balancing tests, the vibration displacement of rotor 8 needs to be constrained within a reasonable range to ensure that the signal collected by the vibration sensor only reflects the vibration caused by the imbalance. However, in the existing testing mechanism, the radial displacement generated by rotor 8 during vibration directly acts on the limiting synchronous belt 3. Although the flexible deformation of the limiting synchronous belt 3 can adapt to the tension, it cannot provide sufficient radial constraint stiffness. When the vibration amplitude is large, rotor 8 may partially lose contact due to the radial displacement exceeding the support range of the limiting synchronous belt 3, resulting in discontinuous support force. This unsteady support will cause abrupt noise in the vibration signal, interfering with the phase detection of the imbalance, and thus affecting the orientation judgment of the counterweight correction.

[0057] Furthermore, the existing testing mechanism suffers from dynamic response lag in its mechanical transmission chain. When the instantaneous load generated by the vibration of rotor 8 is transmitted through the mechanical link of the limiting synchronous belt 3-driven wheel-slider, the inertial mass and elastic deformation of each link cause the tension adjustment to lag behind the change in vibration load. This lag effect keeps the tension of the limiting synchronous belt 3 in a continuous dynamic adjustment, making it impossible to form a stable support state within the vibration cycle. This results in the dynamic characteristics of the testing system changing over time, failing to meet the basic requirements of dynamic balancing testing for system parameter stability.

[0058] Based on this, in the generator dynamic balancing test device provided in the embodiment of the present invention, the synchronous belt 3 is configured to have a fixed section, which wraps around the top of the rotor 8 on the outside during use and is in frictional contact with the rotor 8.

[0059] Specifically, the limiting synchronous belt 3 between the two active tensioning pulleys 406 is a fixed section, which is inverted U-shaped during use and wraps around the top of the rotor 8. This geometric configuration realizes the directional constraint of the contact interface: the two sides of the inverted U-shaped structure form an arc-shaped contact surface with the top of the rotor 8, forming a continuous friction force transmission path in the circumferential direction, while the top arc segment constitutes a radial constraint surface, so that a "drive-constraint" composite mechanical relationship is formed between the fixed section and the rotor 8.

[0060] In terms of the drive mechanism, the inverted U-shaped fixed section utilizes the frictional coupling principle of the limiting synchronous belt 3. When the driving pulley 402 drives the limiting synchronous belt 3, the frictional contact between the fixed section and the top of the rotor 8 generates a tangential driving torque. The inverted U-shaped structure improves the frictional transmission efficiency by increasing the contact arc length. Compared to the point or line contact between the belt and the rotor 8 in traditional free support, the surface contact formed by the inverted U-shape allows for a more uniform distribution of tangential stress, providing a greater ultimate frictional force under the same tension, thereby avoiding slippage of the rotor 8 during acceleration. This surface contact drive mechanism also disperses the driving force to a larger contact interface, reducing local stress concentration and enabling the rotor 8 to obtain a more stable driving torque, providing stable speed conditions for dynamic balance testing.

[0061] In terms of constraint mechanism, the inverted U-shaped topology of the fixed section constructs a rigid constraint boundary for the radial motion of the rotor 8. When the rotor 8 vibrates radially due to imbalance, the top arc of the fixed section directly limits the upward displacement of the rotor 8. This limiting effect is different from the flexible constraint that relies on belt deformation in the prior art. Instead, it provides a hard constraint through the structural stiffness of the fixed section.

[0062] Specifically, the fixed section maintains a nearly constant tension force under the pre-tensioning action of the elastic tensioning wheel 403, causing the top arc segment of the inverted U-shaped structure to form a constraint surface with a certain rigidity. When the rotor 8 vibrates and touches this constraint surface, it will be subjected to a constraint force opposite to the vibration direction, thereby limiting the radial vibration of the rotor 8 within the constraint range of the fixed section. This rigid constraint mechanism can effectively prevent the rotor 8 from detaching from the support surface due to excessive vibration amplitude, ensuring the continuity of the support force.

[0063] Therefore, by using the inverted U-shaped structure of the fixed section, the driving and constraint functions are integrated into the same mechanical interface: in the driving dimension, a stable driving torque is provided through surface contact friction transmission; in the constraint dimension, a stable radial constraint boundary is constructed through a rigid topological structure. This solves the vibration instability problem caused by free support in the existing technology, and ensures the dynamic stability of the test system through a stable tension mechanism. In principle, it achieves the dual goal of "stable support - accurate vibration measurement" required for dynamic balance testing.

[0064] In a further embodiment, due to the processing error of the limiting synchronous belt 3, there is an inconsistency in its thickness. The inconsistency in thickness will lead to uneven distribution of belt stiffness. When the limiting synchronous belt 3 is running at high speed, this uneven stiffness will cause periodic excitation force, which will cause the rotor 8 to vibrate abnormally and affect the accuracy of the test results.

[0065] Based on this, in the generator dynamic balancing test device provided in this embodiment of the invention, the limiting synchronous belt 3 is configured to have an acceleration state and a stable state. The generator dynamic balancing test device also includes an adjustment mechanism, which is configured to adjust the state of the limiting synchronous belt 3. During the acceleration phase of the rotor 8, the limiting synchronous belt 3 is in the acceleration state and is configured to drive the rotor 8 to rotate at an accelerated speed. At this time, the area of ​​the fixed section surrounding the rotor 8 is large. This change in geometric constraint essentially improves the transmission efficiency of frictional torque by increasing the contact arc length. According to the principle of tribology, the increase in contact area makes the tangential contact stress distribution more uniform. Under the same preload conditions, a larger contact area can provide a higher ultimate frictional force, thereby avoiding slippage of the rotor 8 during the acceleration phase. At the same time, the interaction force between the fixed section and the rotor 8 is dispersed and transmitted through a larger contact interface. This distributed force transmission mechanism can reduce local stress concentration, allowing the rotor 8 to obtain a more stable driving torque during acceleration, thereby shortening the acceleration time and improving test efficiency.

[0066] When the rotor 8 accelerates to the preset speed and enters a stable state, the limiting synchronous belt 3 is in a stable state and is configured to drive the rotor 8 to rotate at a constant speed. At this time, the area of ​​the fixed section surrounding the rotor 8 is small. This state transition contains the optimization logic of dynamic characteristics.

[0067] Specifically, reducing the wrapping area can effectively reduce the intensity of the excitation force: on the one hand, the reduction in contact area reduces the range of radial force caused by the difference in belt thickness, reducing the excitation effect of non-uniform stiffness on the vibration of rotor 8; on the other hand, the reduction in radial constraint force weakens the coupled vibration between the belt and rotor 8, making the vibration characteristics of rotor 8 closer to the inherent vibration state caused by its own imbalance, thereby avoiding interference of belt defects on the test signal.

[0068] Therefore, by limiting the state switching of synchronous belt 3, the coupling relationship between contact area and mechanical properties is utilized: in the acceleration stage, the force transmission efficiency is enhanced by increasing the contact area, and the linear growth characteristic of friction torque is used to achieve rapid and stable acceleration; in the stabilization stage, unnecessary coupling is weakened by reducing the contact area, so that the vibration signal of rotor 8 can more purely reflect its own imbalance characteristics.

[0069] Specifically, to facilitate the state switching of the limiting synchronous belt 3, two first sliding grooves 4011 are provided on the bracket 401. The first sliding grooves 4011 extend in the vertical direction and are respectively provided corresponding to two active tensioning wheels 406. During installation, the axle of the active tensioning wheel 406 is slidably inserted into the first sliding groove 4011 to ensure that it can slide along the first sliding groove 4011. The adjustment mechanism is provided to include two third driven wheels 501 and two driving components. Both third driven wheels 501 are provided on the bracket 401, such as... Figure 6As shown, the two third driven wheels 501 are located at the same horizontal height and are symmetrically arranged about the rotor 8. They are both located between the second driven wheel 405 and the driving wheel 402. One of the third driven wheels 501 is located in front of and below the rear of the second driven wheel 405, and the other second driven wheel 405 is located behind and below the front of the second driven wheel 405. The driving component is the first driving cylinder 502. Both first driving cylinders 502 are mounted on the bracket 401. The two first driving cylinders 502 and the two first sliding grooves 4011 are correspondingly arranged. When the first driving cylinder 502 is installed, its output shaft faces downward and is hinged to the axle of the driving tension wheel 406 to ensure that the driving tension wheel 406 can slide along the first sliding groove 4011.

[0070] Optionally, to improve the stability of the active tension wheel 406 during movement, the number of first drive cylinders 502 can be set to four. The four first drive cylinders 502 are divided into two groups. The two first drive cylinders 502 in the same group are symmetrically arranged about the bracket 401, and their output shafts are respectively hinged to both ends of the same active tension wheel 406.

[0071] It is understandable that the first drive cylinder 502 can be configured as any of a hydraulic cylinder, a pneumatic cylinder, or an electric cylinder.

[0072] During use, the active tensioner 406 has corresponding first and second positions before and after sliding. During the acceleration phase of rotor 8, the active tensioner 406 is in the first position, such as... Figure 6 and Figure 7 As shown, at this time, the active tensioning wheel 406 is located at the bottom end of the first groove 4011, restricting the synchronous belt 3 to be in the first state. The restricting synchronous belt 3 is wound around the active wheel 402, the elastic tensioning wheel 403, the first driven wheel 404, the two second driven wheels 405, and the two active tensioning wheels 406. At this time, the area of ​​the fixed section covering the rotor 8 is large, resulting in a large interaction force between the fixed section and the rotor 8, thereby ensuring that the fixed section can stably drive the rotor 8 to accelerate, which is beneficial to improving test efficiency. When the rotor 8 accelerates to the preset speed and enters a stable state, the active tensioning wheel 406 is in the second position, as shown. Figure 8 and Figure 9 As shown, at this time, the active tensioning wheel 406 is located at the top of the first slide groove 4011, restricting the synchronous belt 3 to be in the second state. The synchronous belt 3 is wrapped around the active wheel 402, the elastic tensioning wheel 403, the first driven wheel 404, the two second driven wheels 405 and the two third driven wheels 501. At this time, the area of ​​the fixed section covering the rotor 8 is small, so the interaction force between the fixed section and the rotor 8 is small. On the one hand, it ensures that the rotor 8 can rotate stably, and on the other hand, it can reduce the vibration effect of the rotor 8 caused by the uneven thickness of the belt, which is conducive to improving the accuracy of the test results.

[0073] Therefore, by adjusting the continuous action of the mechanism, the state of the limiting synchronous belt 3 can be switched automatically.

[0074] In a further embodiment, when the rotor 8 vibrates irregularly due to imbalance, the contact area between the fixed section of the limiting synchronous belt 3 and the rotor 8 will be subjected to periodically changing radial and tangential forces. This spatiotemporal difference in dynamic load distribution will cause non-uniform deformation at different positions of the limiting synchronous belt 3, which will in turn cause differences in the thickness direction of the limiting synchronous belt 3: the thinner area of ​​the belt has lower bending stiffness and will produce greater bending deformation when passing through the active tensioning wheel 406. This deformation will generate additional radial impact force on the rotor 8; while the thicker area of ​​the belt has greater stiffness and will generate abrupt contact force when contacting the rotor 8. This excitation force caused by the difference in belt thickness has a clear periodicity, and its frequency is related to the belt rotation speed and thickness fluctuation period, thereby superimposing interference components related to the unbalance amount into the vibration signal of the rotor 8.

[0075] Based on this, in the generator dynamic balancing test device provided in the embodiment of the present invention, the active tensioning wheel 406 is configured to have a fixed and coaxially arranged first sub-wheel 4061 and two second sub-wheels 4062, the two second sub-wheels 4062 are located on both sides of the first sub-wheel 4061, and their diameters are all larger than the first sub-wheel 4061; the third driven wheel 501 has a fixed and coaxially arranged third sub-wheel 5011 and two fourth sub-wheels 5012, the two fourth sub-wheels 5012 are located on both sides of the third sub-wheel 5011, and their diameters are all smaller than the third sub-wheel 5011; the number of limiting synchronous belts 3 is three, the three limiting synchronous belts 3 are arranged side by side, the limiting synchronous belt 3 located in the middle is configured to cooperate with the first sub-wheel 4061 or the third sub-wheel 5011, and the limiting synchronous belts 3 located on both sides are configured to cooperate with the second sub-wheel 4062 or the fourth sub-wheel 5012.

[0076] During use, when the limiting synchronous belt 3 is in an accelerated state, it is wound around the driving pulley 402, the elastic tensioning pulley 403, the first driven pulley 404, the two second driven pulleys 405, and the two driving tensioning pulleys 406. Supported by the second distribution pulley 4062, the limiting synchronous belt 3 on both sides has a greater tension, resulting in greater friction when it contacts the rotor 8, thus serving as the main power source for accelerating the rotor 8. Correspondingly, it is more affected by the irregular vibration of the rotor 8 caused by imbalance, which affects the belt thickness. Conversely, the limiting synchronous belt 3 in the middle has a lower tension, resulting in less friction when it contacts the rotor 8, thus serving as an auxiliary power source for accelerating the rotor 8. Correspondingly, it is less affected by the irregular vibration of the rotor 8 caused by imbalance, which affects the belt thickness.

[0077] When the limiting synchronous belt 3 is in a stable state, it is wound around the driving pulley 402, the elastic tensioning pulley 403, the first driven pulley 404, the two second driven pulleys 405, and the two third driven pulleys 501. With the support of the third pulley 5011, the limiting synchronous belt 3 in the middle has a greater tension, resulting in greater friction when it contacts the rotor 8, thus serving as the main power source for driving the rotor 8 to rotate stably. The limiting synchronous belts 3 on both sides have a smaller tension, resulting in less friction when they contact the rotor 8, thus serving as an auxiliary power source for driving the rotor 8 to rotate stably. Therefore, the rotor 8 can be driven to rotate stably with the limiting synchronous belt 3, which is less affected by the belt thickness, thereby reducing the impact of inconsistent belt thickness on the dynamic balance test results of the rotor 8.

[0078] In a further embodiment, to improve the stability of the timing belt 3 during operation, the diameter difference between the first pulley 4061 and the second pulley 4062 is set to be less than the belt thickness of the timing belt 3; the diameter difference between the third pulley 5011 and the fourth pulley 5012 is also less than the belt thickness of the timing belt 3. The essence of this dimensional constraint is to construct an overlapping interference region in the belt thickness direction, thereby forming a self-limiting mechanical coupling mechanism.

[0079] Specifically, when the timing belt 3 is restricted to bypass the pulleys, the radial displacement of the belt cross-section due to bending is directly related to the diameter of the pulleys. The pulleys with smaller diameters will cause greater bending deformation of the belt. The constraint condition that the diameter difference is less than the belt thickness ensures that the bending trajectories of the belt under the action of different pulleys intersect in the thickness direction. The existence of this overlapping area makes multiple timing belts 3 form a mutually interlocking structural relationship in the thickness direction, which restricts the independent offset of a single timing belt 3 like a mechanical limiting device, thereby improving the stability of the timing belt 3 during operation.

[0080] In other embodiments, to improve the convenience of loading and unloading the rotor 8, a first support 6 is also provided on the test platform 1. The first support 6 is located between the two second supports 201 and is on the same straight line as the two second supports 201, ensuring stable dynamic balancing testing of the rotor 8. The bracket 401 is hinged to the first support 6, allowing the angle between the bracket 401 and the first support 6 to be changed. Thus, when installing or removing the rotor 8, a larger angle can be maintained between the bracket 401 and the first support 6. Figure 1 As shown, this facilitates placing the rotor 8 on the four rollers 202 or removing the rotor 8 from the four rollers 202. During dynamic balancing tests of the rotor 8, a small included angle can be maintained between the support 401 and the first support 6. Figure 3As shown, the outer side of the fixed section can wrap around the top of the rotor 8 and make frictional contact with the rotor 8, ensuring that it can both drive the rotor 8 to rotate and apply external constraints to the rotor 8. The generator dynamic balancing test device is also configured to include a drive assembly 7, which is configured to provide a driving force for the rotation of the support 401.

[0081] Specifically, the drive assembly 7 includes a second drive motor 701, a transmission belt 702, and a fixed pulley 703. The second drive motor 701 is mounted on the first support 6, and a pulley is fixedly sleeved on the motor shaft of the second drive motor 701. The fixed pulley 703 is fixedly mounted on the bracket 401. The transmission belt 702 is wound around the pulley and the fixed pulley 703. In this way, the second drive motor 701 can drive the pulley to rotate, and the pulley can drive the fixed pulley 703 to rotate via the transmission belt 702. Thus, the angle between the bracket 401 and the first support 6 can be changed through the hinged connection between the bracket 401 and the first support 6.

[0082] In a further embodiment, to improve the ease of adjusting the alignment of the timing belt 3 and the center of the rotor 8, the first support 6 is configured to slide in a direction parallel to the axis of the rotor 8.

[0083] Specifically, in this embodiment, a second slide groove 101 is provided on the top of the test platform 1, and the second slide groove 101 extends in a direction parallel to the axis of the rotor 8; a first slider is provided at the bottom of the first support 6, and the first slider is slidably inserted into the second slide groove 101 during installation to ensure that the first support 6 can slide in a direction parallel to the axis of the rotor 8, thereby adjusting the relative position between the limiting synchronous belt 3 and the middle of the rotor 8; a first locking bolt is threaded through the first support 6, and the first locking bolt is configured to form a friction locking engagement with the test platform 1, so that after the limiting synchronous belt 3 and the middle of the rotor 8 are aligned, the first support 6 can be locked on the test platform 1, thereby locking the position of the limiting synchronous belt 3 and improving the stability of the limiting synchronous belt 3 during movement.

[0084] Understandably, the relative position between the limiting synchronous belt 3 and the middle of the rotor 8 can also be adjusted by directly moving the rotor 8.

[0085] In other embodiments, to enable the sliding of the first support 6, a second drive cylinder can be provided on the test platform 1. The output shaft of the second drive cylinder extends in a direction parallel to the axis of the rotor 8 and is fixed on the first support 6, ensuring that the first support 6 can be driven to slide in a direction parallel to the axis of the rotor 8, thereby adjusting and limiting the relative position between the synchronous belt 3 and the middle of the rotor 8.

[0086] Understandably, the second drive cylinder can be configured as any of a hydraulic cylinder, a pneumatic cylinder, or an electric cylinder.

[0087] In other embodiments, to achieve the sliding of the first support 6, a lead screw can be provided on the test platform 1. The lead screw extends in a direction parallel to the axis of the rotor 8 and can rotate around its own axis. During installation, the first support 6 is sleeved on the lead screw and forms a transmission engagement with it, ensuring that the first support 6 can slide in a direction parallel to the axis of the rotor 8, thereby adjusting the relative position between the timing belt 3 and the middle of the rotor 8. Optionally, the lead screw can be rotated manually. Optionally, the lead screw can also be rotated by a third drive motor.

[0088] In other embodiments, the rotor 8 has various specifications, resulting in different lengths. To improve the versatility of the generator dynamic balancing test device, both second supports 201 are configured to slide in a direction parallel to the axis of the rotor 8, so that the distance between the two second supports 201 can be adjusted according to the different lengths of the rotor 8, thereby adapting to rotors 8 of different lengths.

[0089] Specifically, in this embodiment, a second slide groove 101 is provided on the top of the test platform 1, and the second slide groove 101 extends in a direction parallel to the axis of the rotor 8; a second slider is provided at the bottom of each second support 201, and the second slider is slidably inserted into the second slide groove 101 during installation to ensure that the second support 201 can be driven to slide in a direction parallel to the axis of the rotor 8, thereby adjusting the distance between the two second supports 201; a second locking bolt is threaded through each second support 201, and the second locking bolt is configured to form a friction locking engagement with the test platform 1, so that after the two second supports 201 are adjusted to the position, the second supports 201 can be locked on the test platform 1, thereby locking the position of the rotor 202 and improving the support stability of the rotor 8.

[0090] In other embodiments, two third drive cylinders can also be provided to achieve the sliding of the second support 201, with the same principle as above, and will not be described again.

[0091] Understandably, the third drive cylinder can be configured as any of the following: a hydraulic cylinder, a pneumatic cylinder, or an electric cylinder.

[0092] In other embodiments, a lead screw can be provided to enable the sliding of the second support 201, with the same principle as above, and will not be described again.

[0093] In other embodiments, the support component 2 may also be configured to replace the wheel 202 with a bearing.

[0094] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

Claims

1. A generator dynamic balancing testing device, configured to perform dynamic balancing tests on the rotor of a generator; characterized in that, include: The test platform is equipped with support components, a timing belt, a pulley assembly, and an adjustment mechanism. Support components configured to support the rotation of the rotor; A timing belt is set on a test platform, forming a closed motion loop on the test platform. The timing belt has a fixed section, which wraps around the top of the rotor during use and makes frictional contact with the rotor. The pulley assembly is configured to enable the limiting timing belt to form a closed motion loop; The pulley assembly includes a bracket on which a driving pulley, an elastic tensioning pulley, a first driven pulley, two second driven pulleys, and two active tensioning pulleys are rotatably mounted about their own axis. The driving pulley, elastic tensioning pulley, first driven pulley, and two active tensioning pulleys are all located inside the limiting synchronous belt and are in frictional contact with the limiting synchronous belt; the two second driven pulleys are located outside the limiting synchronous belt and are in frictional contact with the limiting synchronous belt; the elastic tensioning pulley is configured to elastically tension the limiting synchronous belt; the two active tensioning pulleys are symmetrically arranged about the rotor. The limiting synchronous belt section between the two active tensioning pulleys is a fixed section with an inverted U-shaped topology. When the rotor vibrates radially due to imbalance, the top arc of the fixed section directly limits the upward displacement of the rotor. The limiting synchronous belt is configured to have an acceleration state and a stable state. In the acceleration state, the limiting synchronous belt is configured to drive the rotor to rotate at an accelerated speed. In the stable state, the limiting synchronous belt is configured to drive the rotor to rotate at a constant speed. Furthermore, in the acceleration state, the area of ​​the fixed section surrounding the rotor is greater than the area of ​​the fixed section surrounding the rotor in the stable state. The adjustment mechanism is configured to adjust the state of the limiting synchronous belt; The active tensioning pulley can slide vertically; the adjusting mechanism includes two third driven pulleys and two driving members. Both third driven pulleys are mounted on a bracket and located inside the limiting synchronous belt, arranged symmetrically about the rotor. The driving members are mounted on the bracket and configured to provide a driving force for the active tensioning pulley to slide vertically. The active tensioning pulley has corresponding first and second positions before and after sliding. In the first position, the limiting synchronous belt is in an accelerated state, and the limiting synchronous belt is wound around the active pulley, the elastic tensioning pulley, the first driven pulley, the two second driven pulleys, and the two active tensioning pulleys. In the second position, the limiting synchronous belt is in a stable state, and the limiting synchronous belt is wound around the active pulley, the elastic tensioning pulley, the first driven pulley, the two second driven pulleys, and the two third driven pulleys. The active tensioning pulley has a fixed and coaxially arranged first pulley and two second pulleys, with the two second pulleys located on both sides of the first pulley and having a diameter larger than the first pulley; the third driven pulley has a fixed and coaxially arranged third pulley and two fourth pulleys, with the two fourth pulleys located on both sides of the third pulley and having a diameter smaller than the third pulley; there are three limiting timing belts, arranged side by side, with the middle limiting timing belt configured to cooperate with either the first or third pulley, and the limiting timing belts on both sides configured to cooperate with either the second or fourth pulleys; The diameter difference between the first and second pulleys is less than the belt thickness of the limiting synchronous belt; the diameter difference between the third and fourth pulleys is less than the belt thickness of the limiting synchronous belt.

2. The generator dynamic balancing test device according to claim 1, characterized in that, The test platform is also equipped with a first support, on which the bracket is hinged; the generator dynamic balancing test device also includes a drive assembly configured to provide the drive force for the rotation of the bracket.

3. The generator dynamic balancing test device according to claim 2, characterized in that, The first support can slide in a direction parallel to the rotor axis.

4. The generator dynamic balancing test device according to claim 1, characterized in that, The support assembly includes two second supports, which are arranged at intervals in a direction parallel to the rotor axis. Each second support is provided with two rollers, the axis of which is parallel to the rotor axis. The rollers can rotate around their own axis. The rollers on different second supports are arranged correspondingly. The two rollers on the same second support are arranged in a direction perpendicular to the rotor axis and form a support area between them. The support area is configured to support the rotor.

5. The generator dynamic balancing test device according to claim 4, characterized in that, Both second supports can slide in a direction parallel to the rotor axis.

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