Semi-active flexible rotor vibration suppression device

Abstract

The utility model relates to a semi-active flexible rotor vibration suppression device, which comprises a rotor structure provided with a rotating shaft, a rotating speed acquisition device, an electric control force application device, a limiting device and a control module, the electric control force application device is connected to one end of the rotating shaft, the limiting device is connected to the other end of the rotating shaft, and the control module is electrically connected with the rotating speed acquisition device. The electric control force application device is electrically connected with the control module; according to the utility model, the energy consumption can be reduced, and the potential risk caused by overheating of the actuator can be avoided during long-time operation.

Description

Technical Field

[0001] The utility model relates to the technical field of rotor vibration suppression, in particular to a semi-active flexible rotor vibration suppression device. Background Art

[0002] The rotor structure is an extremely important component of rotating machinery. With the widespread application of rotating machinery in aerospace, automobiles, turbomachinery and advanced manufacturing, the difficulties in the operating efficiency and stability of rotating machinery caused by the vibration and related noise problems of the rotor structure have become increasingly prominent in these fields. Although reducing the overall mass of the rotor structure can increase the power density of the rotating machinery and the rotation efficiency, the cost is that the structural flexibility of the rotor increases, making it more susceptible to vibration and noise problems. Therefore, researchers have explored various methods to control rotor vibration. These methods can generally be divided into passive, semi-active and active control methods.

[0003] The main limitation of the passive control method is that it cannot effectively adapt to the uncertainties of rotor parameter dynamics and external vibration excitation, but this can be better addressed by adopting semi-active or active control methods.

[0004] Semi-active and active control methods can reduce rotor vibration by adjusting the stiffness and damping of the rotor system or by applying appropriate control forces, such as methods utilizing magnetorheological (MR) dampers, active electromagnetic bearings (AMBs) dampers, and active piezoelectric bearings (AMB) dampers.

[0005] The viscosity characteristics of magnetorheological dampers can be changed by applying a magnetic field, which allows the force applied to the rotor at a specific speed to be varied to achieve appropriate control of rotor vibration. As for active electromagnetic bearing dampers, due to their disadvantage of easily leaking sediment inside the actuator, active piezoelectric bearing dampers have been increasingly used in high-speed rotating machinery in recent years due to their unique characteristics in suppressing rotor vibration. However, active piezoelectric bearing dampers generally require a large actuator force because they must be able to offset the bearing forces caused by the imbalance and deadweight of the rotor system to ensure the suspension and operational stability of the rotor shaft. Therefore, the implementation of active piezoelectric bearing dampers is generally expensive and difficult for heavy industrial rotor systems.

[0006] Inspired by the emergence of active piezoelectric bearing dampers, researchers have explored alternative solutions to piezoelectric actuators. Since 1989, piezoelectric actuators have been used in conjunction with traditional deep groove ball bearings to reduce rotor vibration. This type of actuator consists of a piezoelectric actuator, a traditional deep groove ball bearing, physical sensors (such as displacement sensors, dynamic force sensors, etc.), and a controller. The piezoelectric actuator actively controls the eccentric center of the flexible rotor to the center of the rotation plane to suppress lateral vibration at high speeds.

[0007] However, all of these active control methods share a common disadvantage: they all require real-time changes in control force based on error feedback signals and require continuous activation during machine operation to achieve the set vibration suppression level. This results in relatively high overall power consumption and the potential risk of overheating of the actuator itself during long-term operation. Utility Model Content

[0008] The purpose of the utility model is to overcome the defects of the prior art and provide a semi-active flexible rotor vibration suppression device, which includes a semi-active flexible rotor vibration suppression device and a semi-active flexible rotor vibration suppression method.

[0009] The utility model provides a semi-active flexible rotor vibration suppression device, the technical solution of which is as follows:

[0010] A semi-active flexible rotor vibration suppression device, comprising:

[0011] A rotor structure having a rotating shaft;

[0012] a speed acquisition device, configured to acquire speed information of the rotor structure;

[0013] an electrically controlled force applying device, configured to apply an axial tension to the rotor structure along the rotating shaft according to a call instruction;

[0014] a limiting device, configured to limit the movement of the rotor structure in the direction of the axial tension applied by the electrically controlled force applying device;

[0015] a control module configured to call the electronically controlled force applying device to apply an axial tension with specific requirements to the rotor structure after the rotational speed of the rotor structure is within a predetermined range;

[0016] in,

[0017] The electrically controlled force applying device is connected to one end of the rotating shaft, and the limiting device is connected to the other end of the rotating shaft;

[0018] The control module is electrically connected to the rotation speed acquisition device, and the electric control force application device is electrically connected to the control module.

[0019] The semi-active flexible rotor vibration suppression device proposed in this utility model, without destroying the original rotor system structure, additionally adds a closed-loop control system consisting of a speed acquisition device, an electronically controlled force-applying device, and a control module. The electronically controlled force-applying device is connected to one end of the rotating shaft and applies an axial tension to the rotor structure along the axis of the rotating shaft. The limiting device is connected to the other end of the rotating shaft and can limit the axial movement of the rotor. With the coordination of the two, the structural stiffness of the rotor structure can be changed, thereby causing a change in the resonant frequency of the rotor structure. In addition, with the participation of the control module, after the rotating shaft speed is within a predetermined range, the electronically controlled force-applying device is called to apply an axial tension with specific requirements to the rotor structure, so that the overall power consumption is relatively reduced.

[0020] Since the lateral stiffness of the rotor structure reaches its minimum at the resonant frequency, the vibration amplitude of the rotor structure reaches its peak value under the action of the unbalanced force on the rotor structure, thereby causing serious vibration and noise problems. The semi-active flexible rotor vibration suppression device proposed in this utility model monitors the speed of the rotor structure in real time through a speed acquisition device. Combined with a closed-loop control system, it can be obtained that when the speed is close to the rotor resonance speed, the control module controls the electric control force device to apply axial force to the rotor structure to increase the structural stiffness of the shaft, while bringing about an increase in the resonant frequency; and when the rotor speed is greater than the original resonant frequency of the rotor, the electric control force device releases the axial force to increase the stiffness of the shaft, thereby avoiding structural noise and damage caused by the resonance of the rotor system, and can also alleviate the potential risk of overheating of the actuator (i.e., the electric control force device) itself during long-term operation.

[0021] Based on the semi-active flexible rotor vibration suppression device proposed in the utility model, the stiffness of the rotor structure can be maintained within a relatively high threshold; the dynamically changing shaft stiffness can be used to effectively suppress the vibration of the rotor under steady-state and transient conditions; at the same time, under certain internal parameters and external excitation changes, the efficiency of vibration control can be guaranteed.

[0022] Preferably, the speed acquisition device includes a speed sensor for obtaining the speed of the shaft; thereby, real-time monitoring of the speed of the rotor structure can be achieved, and the collection and transmission of speed information is guaranteed, which is more conducive to the control module's effective grasp of the speed of the rotor structure, thereby providing a basis for controlling the electronically controlled force application device.

[0023] Preferably, the device further comprises a substrate for placing the electrically controlled force applying device and the limiting device, thereby providing support for the electrically controlled force applying device and the limiting device, and ensuring their stable and orderly operation.

[0024] Preferably, the electrically controlled force-applying device includes a first bearing base, a first bearing, at least three hydraulic actuators and a thrust pin. The bottom of the first bearing base is connected to the base plate. The first bearing base is provided with a first mounting hole extending axially through the rotating shaft. The first bearing is fixed to the first mounting hole. The rotating shaft passes through the first bearing and its end is located outside the first bearing base. At least three hydraulic actuators are circumferentially distributed around the rotating shaft. The actuator of each hydraulic actuator is keyed to the rotating shaft and is also electrically connected to the control module. The thrust pin is used to connect the end of the rotating shaft to the regulating valve of each hydraulic actuator. Since the actuator of each hydraulic actuator is keyed to the rotating shaft, its regulating valve is connected to the rotating shaft through the thrust pin, and the stiffness of the rotating shaft in the critical speed range can be changed by the displacement of the regulating valve of the hydraulic actuator along the axial direction of the rotating shaft, ensuring that it always maintains a high stiffness from the low speed to the high speed range, providing control guarantee for reducing the resonance amplitude of the rotor structure at the critical speed.

[0025] Preferably, all the regulating valves (332) of the hydraulic actuators are provided with force sensors for obtaining information on the force applied by the regulating valves to the rotating shaft, and the force sensors are electrically connected to the control module; thereby facilitating real-time acquisition of information on the force applied by the hydraulic actuator to the rotor structure, and transmitting the obtained force information to the control module, providing feedback information on the results of the control module's manipulation of the hydraulic actuator, so as to achieve real-time updates of the manipulation of the hydraulic actuator.

[0026] Preferably, the electrically controlled force-applying device further comprises a thrust bearing and a connecting piece, wherein the thrust bearing is sleeved on the end of the rotating shaft and connected to the top of the regulating valve of all the hydraulic actuators, and the connecting piece is connected to the thrust bearing; thereby not only increasing the load of the hydraulic actuator to a certain extent to enhance its execution stability and appropriately alleviate the vibration of the rotating shaft, but also making the top surface of the rotating shaft end portion located in the limited area within the thrust bearing, indirectly setting a unique access end for the rotating shaft.

[0027] Preferably, the limiting device includes a second bearing base, a second bearing and a limiting pin, the bottom of the second bearing base is connected to the base plate, the second bearing base is provided with a second mounting hole that passes through the axial direction of the rotating shaft, the second bearing is fixed on the second mounting hole, the rotating shaft passes through the second bearing and its end is located outside the second bearing base, the limiting pin is arranged at the end of the rotating shaft, and is used to limit the movement of the rotating shaft along the direction in which the regulating valves of the hydraulic actuators exert force on it; thereby, the axial movement of the rotating shaft can be restricted, especially when the hydraulic actuators apply axial tension to the rotating shaft, the rotating shaft (also the rotor structure) is restricted in its axial movement, thereby achieving the purpose of controlling the structural stiffness of the rotating shaft and even the rotor structure to control the vibration of the rotor.

[0028] Preferably, the first bearing and the second bearing are both deep groove ball bearings; thereby effectively maintaining the operation of the rotating shaft, and also improving the rotation efficiency and reducing heat loss to a certain extent.

[0029] Preferably, the control module includes:

[0030] a controller configured to issue a call instruction to the hydraulic actuators to apply axial tension to the rotor structure when the rotation speed of the rotating shaft is within a predetermined range, and to update the content of the call instruction based on force information applied by the hydraulic actuators, and not issue the call instruction when the rotation speed of the rotating shaft is not within the predetermined range;

[0031] A signal amplifier is configured to perform real-time signal amplification processing on the call instruction issued by the controller so as to transmit the signal to the hydraulic actuators;

[0032] in,

[0033] The controller is electrically connected to the speed acquisition device and the force sensor, and the signal amplifier is electrically connected to the actuators of the hydraulic actuators;

[0034] Furthermore, after the force sensor obtains the force information of the hydraulic actuator and the speed sensor obtains the rotor speed signal, the controller compares the rotor speed with the defined trigger interval (i.e., the predetermined interval). If the rotor speed is lower than the lower limit of the predetermined interval or higher than the upper limit of the predetermined interval, the hydraulic actuator will be controlled not to apply tension to the rotor, and the rotor will exhibit its original stiffness. If it is detected that the rotor speed is in the predetermined interval, the hydraulic actuator will be controlled to apply tension to the rotor, and the rotor will exhibit low stiffness. This control mechanism of actively tuning the rotor stiffness can maintain the low stiffness characteristics of the rotor stiffness at the resonant frequency, suppress excessive vibration of the rotor structure when passing through the natural frequency at high speed, and increase the rotor speed range. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] Figure 1 This is a structural schematic diagram of a semi-active flexible rotor vibration suppression device in Example 1 of the present utility model;

[0036] Figure 2 This is a side view of a semi-active flexible rotor vibration suppression device in Example 1 of the present utility model;

[0037] Figure 3 This is a top view of a semi-active flexible rotor vibration suppression device in Example 1 of the present utility model;

[0038] Figure 4 This is a cross-sectional view of a semi-active flexible rotor vibration suppression device in Example 1 of the present utility model;

[0039] Figure 5 This is a cross-sectional view of the electric-controlled force-applying device in the first embodiment of the present invention;

[0040] Figure 6 This is a cross-sectional view of the limiting device in Example 1 of the present utility model;

[0041] Figure 7 This is a control principle diagram of a semi-active flexible rotor vibration suppression device in Example 1 of the present utility model;

[0042] Figure 8 This is a schematic diagram of the control circuit structure of a semi-active flexible rotor vibration suppression device in Example 1 of the present utility model;

[0043] Figure 9 This is the control law image of the controller in Example 1 of the present utility model.

[0044] Among them, the numbers marked in the figure represent: 1. Rotor structure: 11. Rotating shaft; 2. Speed ​​acquisition device: 3. Electronically controlled force device: 31. First bearing base; 311. First mounting hole; 32. First bearing; 33. Hydraulic actuator; 331. Actuator; 332. Control valve; 333. Force sensor; 34. Thrust pin; 35. Thrust bearing; 36. Connector; 4. Limiting device: 41. Second bearing base; 411. Second mounting hole; 42. Second bearing; 43. Limiting pin; 5. Control module: 51. Controller; 52. Signal amplifier; 6. Substrate. DETAILED DESCRIPTION

[0045] The following will use an embodiment and combine with the drawings in the embodiment of the present invention to clearly and completely describe the technical solution of the present invention.

[0046] Example 1

[0047] The present invention provides a semi-active flexible rotor vibration suppression device, which includes:

[0048] A rotor structure 1 having a rotating shaft 11;

[0049] The speed acquisition device 2 is configured to obtain the speed information of the rotor structure 1;

[0050] The electrically controlled force applying device 3 is configured to apply axial tension to the rotor structure 1 along the rotating shaft 11 according to a call instruction;

[0051] The limiting device 4 is configured to limit the movement of the rotor structure 1 in the direction of the axial tension applied by the electronically controlled force applying device 3;

[0052] The control module 5 is configured to receive the rotational speed information and, when the rotational speed of the rotor structure 1 is within a predetermined range, call the electronically controlled force applying device 3 to apply an axial tension with specific requirements to the rotor structure 1;

[0053] in,

[0054] The electric-controlled force-applying device 3 is connected to one end of the rotating shaft 11, and the limiting device 4 is connected to the other end of the rotating shaft 11;

[0055] The control module 5 is electrically connected to the rotation speed acquisition device 2 , and the electric-controlled force application device 3 is electrically connected to the control module 5 .

[0056] In this embodiment, the rotating shaft 11 is a flexible shaft. As an implementation, in this embodiment, the speed acquisition device 2 includes a speed sensor for measuring the speed of the rotating shaft 11, such as a gyroscope or a machine vision sensor for measuring angular velocity. The speed sensor is electrically connected to the control module 5, and thus constantly collects angular velocity information of the rotating shaft 11 driven by the rotor structure 1. This information is then transmitted to the control module 5, providing a basis for its operation.

[0057] As an implementation mode, in this embodiment, the device further includes a substrate 6 for placing the electric-controlled force-applying device 3 and the limiting device 4, and the shape of the substrate 6 is rectangular, and the electric-controlled force-applying device 3 and the limiting device 4 are installed and distributed on both sides of the central axis of the substrate 6.

[0058] As an implementation mode, in this embodiment, the electrically controlled force-applying device 3 specifically includes a first bearing base 31, a first bearing 32, at least three hydraulic actuators 33 and a thrust pin 34, wherein the number of hydraulic actuators 33 used in this embodiment is 3, the bottom of the first bearing base 31 is connected to the base plate 6, the first bearing base 31 is provided with a first mounting hole 311 extending axially through the rotating shaft 11, the first bearing 32 is fixed on the first mounting hole 311, the rotating shaft 11 passes through the first bearing 32 and its end is located outside the first bearing base 31; the hydraulic actuator 3 is a Siemens hydraulic actuator, including an actuator 331 and a regulating valve 332 connected thereto, all the hydraulic actuators 33 are circumferentially distributed around the rotating shaft 11, the actuator 331 of each hydraulic actuator 33 is key-connected (such as a flat key link) to the rotating shaft 11, and is also electrically connected to the control module 5; the thrust pin 34 is provided on the rotating shaft 11, and is used to connect the end of the rotating shaft 11 with the regulating valve 332 of each hydraulic actuator 33.

[0059] In addition, in this embodiment, the regulating valves 332 of all hydraulic actuators 33 are provided with force sensors 333 for obtaining the force information of the regulating valves 332 on the rotating shaft 11. These force sensors 333 are all electrically connected to the control module 5 to transmit the force information of the regulating valves 332 to the control module 5 in real time.

[0060] In this embodiment, the electrically controlled force-applying device 3 further includes a thrust bearing 35 and a connecting member 36. The thrust bearing 35 is sleeved on the end of the rotating shaft 11, and its outer ring is connected to the top of the regulating valve 332 of all the hydraulic actuators 33. The connecting member 36 can be a rectangular plate, and the connecting member 36 is connected to the outer ring of the thrust bearing 35.

[0061] As an implementation mode, in this embodiment, the limiting device 4 specifically includes a second bearing base 41, a second bearing 42 and a limiting pin 43. The bottom of the second bearing base 41 is connected to the base plate 6. The second bearing base 41 is provided with a second mounting hole 411 that passes through the axial direction of the rotating shaft 11. The second bearing 42 is fixed on the second mounting hole 411. The rotating shaft 11 passes through the second bearing 42 and its end is located outside the second bearing base 41. The limiting pin 43 is set at the end of the rotating shaft 11, and is used to limit the movement of the rotating shaft 11 along the direction in which the regulating valve 332 of the hydraulic actuators 33 applies force to it.

[0062] Specifically, the first bearing 32 and the second bearing 42 are both deep groove ball bearings. In this embodiment, the stop pin 43 is a cylindrical pin that extends through the rotating shaft 11, with both ends located outside the rotating shaft. Its length is greater than the diameter of the second mounting hole 411 provided in the second bearing base 41. This allows the second bearing base 41 to press against the stop pin 43 to limit its movement when the hydraulic actuator 33 applies an axial pulling force along the rotating shaft 11 to the rotor structure 1, causing the rotor structure 1 to move axially along the rotating shaft 11.

[0063] As an implementation manner, in this embodiment, the control module 5 includes:

[0064] The controller 51 is configured to issue a call instruction to the hydraulic actuators 33 to apply axial tension to the rotor structure 1 when the rotation speed of the rotating shaft 11 is within a predetermined range, and to update the content of the call instruction based on the force information applied by the hydraulic actuators 33, and not issue the call instruction when the rotation speed of the rotating shaft 11 is not within the predetermined range;

[0065] The signal amplifier 52 is configured to amplify the call instruction issued by the controller 51 in real time and transmit it to the hydraulic actuators 33;

[0066] in,

[0067] The controller 51 is electrically connected to the rotation speed acquisition device 2 and the force sensor 333 , and the signal amplifier 52 is electrically connected to the actuators 331 of the hydraulic actuators 33 .

[0068] As an implementation mode, in this embodiment, the control model embedded in the controller 51 is a square wave function control model. The square wave function control model can be specifically expressed as follows:

[0069]

[0070] Among them, P t To call the hydraulic actuator to apply the control axial force to the rotor structure 1; Ω, Ω s ,Ω e They are respectively the actual rotation speed of the rotor structure 1, the starting rotation speed when the axial execution mechanism is activated (ie the lower limit of the predetermined interval) and the release rotation speed when the axial execution is terminated (ie the upper limit of the predetermined interval).

[0071] If the mass of the turntable of the rotor structure 1 is m, the stiffness components of the shaft 11 in each direction are k1, k2, k3, and k4, which can be deduced from formula (1).

[0072]

[0073] Where l is the length of the shaft 11, a and b are the distances from the center of the turntable to the left and right ends respectively, and P is the value of the axial hydraulic pressure. The structural damping coefficient of the shaft 11 is C, which can be derived from formula (2):

[0074] C=a0M+a1K (2) Where a0 and a1 are constants related to the material properties of the shaft, and their calculation method is derived from formula (3):

[0075]

[0076] Based on the first and second natural frequencies of the shaft and the damping coefficient, the values ​​of a0 and a1 can be calculated, and the structural damping coefficient can be derived. By substituting the turntable mass, moment of inertia, polar moment of inertia, rotor eccentricity, and rotor speed into formula (4), the turntable lateral displacement at a specific speed can be calculated, as well as the frequency response diagram.

[0077]

[0078] The activation speed is proportional to the required vibration suppression Calculate. By using formula (4), the starting speed Ω can be numerically solved. s and the required axial load P t The value of .

[0079] The control block diagram of this embodiment is as follows Figure 7 As shown in FIG, the entire control block diagram is composed of a single control loop consisting of a speed acquisition device 2 (a speed sensor in this embodiment), a controller 51, a signal amplifier 52, a hydraulic actuator 33, and a force sensor 333. As can be seen from the figure, in this control loop, when the control model is activated, the speed sensor will collect the speed of the rotor structure 1 in real time, and input the obtained speed signal into the controller 51 in real time. The controller 51 will compare whether the current speed is within a predetermined range, that is, whether the actual speed satisfies the inequality: Ω s <Ω<Ω e The controller 51 executes its execution strategy through the piecewise function corresponding to the above square wave function model, and the axial force P can only be activated when the rotor runs within a certain speed range (ie, satisfies the above inequality).

[0080] When the axial force P is activated, the rotor structure 1 is excited by F x 、F y The axial load P of 11 is applied to the rotor structure 1 through the hydraulic actuator 33 called by the controller 51, and the speed sensor collects the real-time angular velocity Ω of the rotor structure 1 and feeds it back to the controller 51. At the same time, the force sensor 333 also feeds back the force information of the hydraulic actuator 33 to the controller 51. The controller 51 updates the control instruction according to the obtained force information to activate the appropriate axial load P, and finally achieves the control of the axial force P.t The level of rotation brings about changes in the shaft stiffness.

[0081] The target of the controller 51 is based on the starting speed Ω when the axial actuator is activated. s , especially when the rotor structure 1 runs close to the end point of the predetermined interval, the fundamental resonant frequency of the rotor structure 1 is tuned to be away from the running speed of the rotor, and then based on the release speed Ω e , releasing the axial load and allowing the shaft stiffness to return to its original value.

[0082] Figure 9 is the control law of the controller 51, in which the rotor structure 1 has an axial force at the initial speed Ω e The intersection point is x ni By adding x ni Maximum lateral vibration displacement of rotor structure 1 at a specific turntable offset Normalization is performed, parameters Indicates the worst rotor vibration suppression ratio under different axial forces and is used as a benchmark for control performance evaluation. In order to achieve the required vibration suppression ratio, Figure 9 Shows the ratio of vibration suppression required Required axial load P t and axial load cut-off speed Ω e The relationship between the release speed Ω can be directly determined from it e and the required axial load P t In addition, the starting speed Ω s The choice of is a balance between achieving the best vibration control performance in the low frequency range and minimizing the control energy consumption. However, in order to ensure adequate vibration control performance in the low frequency range below the fundamental resonance frequency, it is necessary to ensure that at the starting speed Ω s The stiffness of the shaft 11 is at least equal to the release speed Ω e The stiffness of the rotating shaft 11 is the same as that of the rotor structure 1, so as to avoid excessive vibration of the rotor structure 1 caused by passing through the resonance interval.

[0083] Starting speed Ω s The choice of has an important influence on the vibration performance in the low frequency region, because as the axial load increases, the s <Ω<Ω e The defined activation range is expanded accordingly, which leads to an increase in control energy consumption. Therefore, the starting speed Ω s The choice of has a significant impact on the vibration control performance in the low frequency range, and the release speed Ω e This is related to the worst rotor vibration suppression ratio over the operating bandwidth of the entire rotor structure 1 .

[0084] As an implementation method, in the rotor structure 1 used in this embodiment, the shaft 11 is 460 mm long and has a shaft radius of 10 mm. A disk with a diameter of 150 mm and a thickness of 10 mm is used as the turntable. With this rotor structure 1 as the control object, normalized analysis is performed to obtain the rotor speed vs. amplitude frequency response and time domain control law. It can be found that the rotor vibration amplitude is Ω at the critical speed and release speed, respectively. e The amplitude values ​​obtained are 0.305 and 0.24, respectively. Compared with the uncontrolled rotor system, the vibration amplitudes are reduced by 76% and 69.5%, respectively. The bandwidth for notifying the control system to activate only accounts for 11.2% of the entire operating bandwidth, avoiding the activation of the full-domain bandwidth, achieving effective vibration suppression and reducing the control energy consumption of the controller.

[0085] Although the embodiments of the present invention have been shown and described, it will be apparent to those skilled in the art that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present invention. The scope of the present invention is defined by the appended claims and their equivalents.

Claims

1. A semi-active flexible rotor vibration suppression device, Features: The vibration suppression device comprises: A rotor structure (1) provided with a rotating shaft (11); A rotation speed acquisition device (2) is configured to acquire rotation speed information of the rotor structure (1); An electrically controlled force applying device (3) is configured to apply an axial pulling force to the rotor structure (1) along the rotating shaft (11) according to a call instruction; A limiting device (4) is configured to limit the movement of the rotor structure (1) in the direction of the axial tension applied by the electrically controlled force applying device (3); A control module (5) is configured to receive the rotational speed information and, when the rotational speed of the rotor structure (1) is within a predetermined range, call the electrically controlled force application device (3) to apply an axial tension to the rotor structure (1); in, The electrically controlled force applying device (3) is connected to one end of the rotating shaft (11), and the limiting device (4) is connected to the other end of the rotating shaft (11); The control module (5) is electrically connected to the rotation speed acquisition device (2), and the electric control force application device (3) is electrically connected to the control module (5).

2. The semi-active flexible rotor vibration suppression device according to claim 1, Features: The rotation speed acquisition device (2) comprises a rotation speed sensor for measuring the rotation speed of the rotating shaft (11).

3. The semi-active flexible rotor vibration suppression device according to claim 1 or 2, Features: The vibration suppression device also includes a base plate (6) for arranging the electric-controlled force-applying device (3) and the limiting device (4).

4. The semi-active flexible rotor vibration suppression device according to claim 3, Features: The electrically controlled force applying device (3) comprises a first bearing base (31), a first bearing (32), at least three hydraulic actuators (33) and a thrust pin (34); the bottom of the first bearing base (31) is connected to the base plate (6); the first bearing base (31) is provided with a first mounting hole (311) extending axially through the rotating shaft (11); the first bearing (32) is fixed to the first mounting hole (311); the rotating shaft (11) passes through the first bearing (32) and its end is located outside the first bearing base (31); at least three hydraulic actuators (33) are circumferentially distributed around the rotating shaft (11); the actuator (331) of each hydraulic actuator (33) is keyed to the rotating shaft (11) and is also electrically connected to the control module (5); the thrust pin (34) is used to connect the end of the rotating shaft (11) to the regulating valve (332) of each hydraulic actuator (33).

5. The semi-active flexible rotor vibration suppression device according to claim 4, Features: The regulating valves (332) of all the hydraulic actuators (33) are provided with force sensors (333) for obtaining information on the force applied by the regulating valves (332) to the rotating shaft (11); the force sensors (333) are electrically connected to the control module (5).

6. The semi-active flexible rotor vibration suppression device according to claim 5, Features: The electrically controlled force applying device (3) further comprises a thrust bearing (35) and a connecting piece (36); the thrust bearing (35) is sleeved on the end of the rotating shaft (11) and connected to the top of the regulating valve (332) of all the hydraulic actuators (33); and the connecting piece (36) is connected to the thrust bearing (35).

7. The semi-active flexible rotor vibration suppression device according to claim 4, 5 or 6, Features: The limiting device (4) comprises a second bearing base (41), a second bearing (42) and a limiting pin (43); the bottom of the second bearing base (41) is connected to the base plate (6); the second bearing base (41) is provided with a second mounting hole (411) extending axially through the rotating shaft (11); the second bearing (42) is fixed to the second mounting hole (411); the rotating shaft (11) passes through the second bearing (42) and an end thereof is located outside the second bearing base (41); the limiting pin (43) is arranged at the end of the rotating shaft (11) and is used to limit the movement of the rotating shaft (11) in the direction in which the regulating valve (332) of the hydraulic actuator (33) applies force to it.

8. The semi-active flexible rotor vibration suppression device according to claim 7, Features: The first bearing (32) and the second bearing (42) are both deep groove ball bearings.

9. The semi-active flexible rotor vibration suppression device according to claim 5, Features: The control module (5) includes: The controller (51) is configured to issue a call instruction to call the hydraulic actuator (33) to apply axial tension to the rotor structure (1) when the rotation speed of the rotating shaft (11) is within a predetermined range, and to update the content of the call instruction according to the force application information of the hydraulic actuator (33), and not to issue the call instruction when the rotation speed of the rotating shaft (11) is not within the predetermined range; A signal amplifier (52) is configured to perform real-time signal amplification processing on the call instruction issued by the controller (51) so as to transmit the signal to the hydraulic actuators (33); in, The controller (51) is electrically connected to the rotation speed acquisition device (2) and the force sensor (333), and the signal amplifier (52) is electrically connected to the actuator (331) of the hydraulic actuator (33).

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