Variable damping ball screw inertia damper and method therefor

Abstract

The present invention provides a variable damping ball screw inertia damper and a method therefor. The variable damping ball screw inertia damper comprises an axial compression structure. A converter is slidably disposed in a penetrating manner in the middle of the axial compression structure. The converter reciprocates within the axial compression structure in an axial direction by means of springs. The converter comprises a support cavity structure. An angular contact ball bearing is fixedly arranged in the middle of the support cavity structure. The angular contact ball bearing is coaxially and penetratingly provided with a ball screw. An upper section of the ball screw is slidably sleeved on the angular contact ball bearing. A lower section of the ball screw is threadedly engaged with the axial compression structure. An energy dissipation flywheel is fixedly connected to a bottom end of the ball screw. The present application solves the technical problem in the prior art of the inability to effectively deal with pipe vibration.

Description

Variable damping ball screw inertial damper and method TECHNICAL FIELD

[0001] The present application belongs to the field of variable damping ball screw inertial damper and method. BACKGROUND

[0002] In a pipeline system, the change of valve state and the sudden change of pipeline diameter often cause pulsating impact, resulting in pipeline vibration problems. Specifically, when a hydraulic valve is suddenly opened, the working medium near the valve, which was originally in a static state, will quickly flow, and the pressure energy will be converted into kinetic energy, resulting in a sharp drop in pressure near the valve. The working medium far from the valve has not yet caught up due to inertia, so the pressure is relatively high. This pressure difference will form a pressure wave in the pipeline and propagate along the pipeline, thereby generating a pulsating impact. Conversely, when the valve is suddenly closed, the speed of the working medium at the valve immediately becomes zero, while the working medium far from the valve continues to move towards the valve due to inertia, causing extrusion to the working medium near the valve, converting kinetic energy into pressure energy. This pressure energy, after hitting the closed valve, will propagate in the opposite direction and form a pulsating impact. In a pipeline system, due to design or installation needs, the diameter of the pipeline may change. When the fluid flows through these diameter-changing positions, the flow rate and pressure distribution of the fluid will change significantly. At the position where the diameter decreases, the flow rate of the fluid increases and the pressure decreases; while at the position where the diameter increases, the flow rate of the fluid slows down and the pressure rises. This change in flow rate and pressure will form a pressure wave in the pipeline, thereby causing a pulsating impact.

[0003] Currently, the main method to control pipeline vibration is to install a tuned mass damper or a damper externally. However, conventional dampers usually need to be grounded for use, with limited application range. For low-frequency vibration, a tuned mass damper needs to be designed, usually by increasing the tuning mass or reducing the structural stiffness to meet the tuning conditions and effectively control the vibration. SUMMARY

[0004] To solve the problems in the prior art, the present application provides a variable damping ball screw inertial damper and method to solve the technical problem that the existing related technology cannot effectively solve the pipeline vibration.

[0005] To achieve the above-mentioned purpose, the present application provides the following technical solutions:

[0006] A variable damping ball screw inertial damper, comprising an axial compression structure, a converter is slidably arranged in the middle of the axial compression structure, and the converter reciprocates along the axial direction in the axial compression structure along the axial direction through a spring.

[0007] The converter includes a support cavity structure, an angular contact ball bearing is fixedly arranged in the middle of the support cavity structure, a ball screw is coaxially arranged through the angular contact ball bearing, the upper segment of the ball screw is sleeved with the angular contact ball bearing in a sliding mode, the lower segment of the ball screw is threadedly engaged with the axial compression structure, and the bottom end of the ball screw is fixedly connected with an energy consumption flywheel.

[0008] Further, the axial compression structure includes an upper top plate and a lower top plate, two parallel arranged connecting rods are arranged through the upper top plate and the lower top plate, and the ends of the connecting rods are provided with fixing members.

[0009] The connecting rods are each provided with two segments of springs, and the two springs on the same connecting rod are arranged with the support cavity structure of the converter.

[0010] Further, the axial compression structure further includes a screw nut fixedly arranged on the lower top plate close to the converter, and the screw nut is threadedly engaged with the ball screw.

[0011] Further, the total stiffness of the two springs on the same connecting rod is the same.

[0012] Further, two linear bearings are fixedly arranged in the support cavity structure, the linear bearings are arranged on both sides of the angular contact ball bearing and are sleeved with the axial compression structure in a sliding mode.

[0013] Further, a plurality of additional mass blocks are detachably arranged in the support cavity structure, and the plurality of additional mass blocks are symmetrically arranged along the center of the support cavity structure.

[0014] Further, a limiting block is arranged at the top of the ball screw, and the bottom of the limiting block abuts against the top of the support cavity structure.

[0015] Further, the upper segment of the ball screw is a light shaft, and the lower segment is a threaded shaft.

[0016] Further, the energy consumption flywheel is fixedly connected to the bottom end of the ball screw through a nut.

[0017] A method of a variable-damping ball screw inertial damper includes the following steps:

[0018] When the axial compression structure is subjected to a pipeline pulsation impact, the received pulsation impact is transmitted downward to the converter, and the spring buffers and dissipates energy by deformation to the axial force;

[0019] When the converter is subjected to a pulsation impact by the spring, the converter drives the ball screw to move up and down along the axial direction and rotate, and the ball screw rotates and dissipates energy through the energy consumption flywheel in the process of rotation.

[0020] Compared with the prior art, the present application has the following beneficial technical effects:

[0021] The present application provides a variable damping ball screw inertial damper, comprising an axial compression structure, a converter is slidably arranged in the middle of the axial compression structure, the converter reciprocates in the axial compression structure along the axial direction by a spring; the converter comprises a support cavity structure, an angular contact ball bearing is fixedly arranged in the middle of the support cavity structure, a ball screw is coaxially arranged through the angular contact ball bearing, the upper segment of the ball screw is sleeved with the angular contact ball bearing in a sliding manner, the lower segment of the ball screw is threadedly engaged with the axial compression structure, and an energy-consuming flywheel is fixedly connected to the bottom end of the ball screw; the axial force in the pulsating impact of the pipeline is buffered and consumed by the axial compression mechanism, since the lower segment of the ball screw is threadedly engaged with the axial compression structure, the converter drives the ball screw to rotate downward, and the ball screw drives the energy-consuming flywheel to rotate and consume energy in the process of self-rotation, the pulsating impact is converted into axial force and radial force, and targeted energy consumption is performed through the spring and the energy-consuming flywheel, thereby solving the technical problem that the pipeline vibration cannot be effectively solved in the prior art.

[0022] Further, the total stiffness of the two springs on the same connecting rod is the same, which can improve stability and uniform load distribution.

[0023] The present application provides a method of a variable damping ball screw inertial damper, comprising the following steps: when the axial compression structure is subjected to pipeline pulsating impact, the pulsating impact is transmitted downward to the converter, and the axial force is buffered and consumed by deformation of the spring; when the converter is subjected to the pulsating impact caused by the spring, the converter drives the ball screw to rotate downward, and the ball screw rotates and consumes energy through the energy-consuming flywheel in the process of self-rotation; the method can effectively convert the pulsating impact into axial force and radial force, and perform targeted energy consumption through the spring and the energy-consuming flywheel, thereby solving the technical problem that the pipeline vibration cannot be effectively solved in the prior art. BRIEF DESCRIPTION OF DRAWINGS

[0024] Fig. 1 shows a structural schematic diagram of the variable damping ball screw inertial damper of the present disclosure;

[0025] Fig. 2 shows a partial sectional view of the variable damping ball screw inertial damper of the present disclosure;

[0026] Fig. 3 shows a structural schematic diagram of the converter of the present disclosure.

[0027] Fig. 4 shows a force schematic diagram of the inertial damper of the present disclosure under the action of a base excitation.

[0028] In the drawings:

[0029] 1 connecting rod; 2 lower top plate; 3 bearing end cover; 4 additional mass; 5 screw nut; 6 upper top plate; 7 ball screw; 8 energy dissipation flywheel; 9 angular contact ball bearing; 10 linear bearing; 11 spring. DETAILED DESCRIPTION

[0030] Hereinafter, certain exemplary embodiments will be described simply. As can be recognized by those skilled in the art, the described embodiments can be modified in various different ways without departing from the spirit or scope of the present application. Therefore, the drawings and descriptions are to be regarded as illustrative in nature rather than restrictive.

[0031] In the description of the present application, it is to be understood that the orientations or positional relationships indicated by the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", and the like are based on the orientations or positional relationships shown in the drawings, and are merely for the purpose of facilitating the description of the present application and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be construed as limiting the present application.

[0032] In addition, the terms "first", "second", etc. are used only for the purpose of description and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, the features defined as "first", "second" can explicitly or implicitly include one or more of the features. In the description of the present application, the meaning of "a plurality of" is two or more, unless otherwise explicitly specified and limited.

[0033] In the present application, unless otherwise explicitly specified and limited, the terms "mounting", "connection", "connection", "fixing", and the like should be understood broadly, for example, it can be fixedly connected, or it can be detachably connected, or it can be integrated; it can be mechanically connected, or it can be electrically connected, or it can be communicated; it can be directly connected, or it can be indirectly connected through an intermediate medium; it can be the internal communication of two elements or the interaction relationship between two elements. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0034] In the present application, unless otherwise explicitly specified and limited, "on" or "under" of a first feature to a second feature can include that the first and second features are in direct contact, or can include that the first and second features are not in direct contact but are in contact through another feature between them. Moreover, "on", "above" and "over" of a first feature to a second feature includes that the first feature is directly above and obliquely above the second feature, or only indicates that the first feature is horizontally higher than the second feature. "Under", "below" and "underneath" of a first feature to a second feature includes that the first feature is directly above and obliquely above the second feature, or only indicates that the first feature is horizontally lower than the second feature.

[0035] It should be understood that the terms "comprises" and "comprising" when used in this specification and the following claims, indicate the presence of the described features, integers, steps, operations, elements, and / or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and / or groups thereof.

[0036] It should also be understood that the terms used in the present application specification are only for the purpose of describing particular embodiments and are not intended to limit the present application. As used in the present application specification and the following claims, unless otherwise clearly indicated by the context, the singular forms "a", "an" and "the" are intended to include the plural forms as well.

[0037] It should be further understood that the term "and / or" used in the present application specification and the following claims refers to any combination of one or more of the associated listed items and all possible combinations, and includes these combinations.

[0038] Various structural diagrams according to the disclosed embodiments of the present application are shown in the accompanying drawings. These drawings are not drawn to scale, in which certain details are exaggerated for the purpose of clarity and certain details can be omitted. The shapes of various regions, layers and their relative sizes and positional relationships shown in the drawings are only exemplary, and in actuality can be deviated due to manufacturing tolerances or technical limitations, and regions / layers with different shapes, sizes and relative positions can be additionally designed by those skilled in the art according to actual needs.

[0039] The embodiments of the present application are described in detail below with reference to the accompanying drawings.

[0040] Figure 1 shows a variable damping ball screw inerter according to an embodiment of the present disclosure, as shown in Figure 1, comprising an axial compression structure, a converter is slidably arranged in the middle of the axial compression structure, the converter reciprocates in the axial compression structure along the axial direction by spring 11;

[0041] The converter includes a support cavity structure, an angular contact ball bearing 9 is fixedly arranged in the middle of the support cavity structure, a ball screw 7 is coaxially arranged through the angular contact ball bearing 9, the upper section of the ball screw 7 is sleeved with the angular contact ball bearing 9, the lower section of the ball screw 7 is threadedly engaged with the axial compression structure, and an energy consumption flywheel 8 is fixedly connected to the bottom end of the ball screw 7.

[0042] It should be noted that in the embodiments of the present disclosure, the variable damping ball screw inertial damper is generally arranged at a pipe diameter mutation of a pipeline system, near a valve, at a pipe fitting such as an elbow, a tee, and / or at an inlet or outlet of a power equipment such as a compressor or a pump; when connected, welding or a connecting piece such as a bolt structure can be used for rigid connection to improve the conduction of the pulsation impact.

[0043] It should be further noted that the single-row or double-row angular contact ball bearing is used in the embodiments, which can bear a combined load, and the double-row angular contact ball bearing can bear a large radial load, a radial and axial combined load, and a torque load, and limit the axial displacement of the shaft in two directions.

[0044] Preferably, in some embodiments, the axial compression structure includes an upper top plate 6 and a lower top plate 2, two parallel connecting rods 1 are arranged through the upper top plate 6 and the lower top plate 2, and the ends of the connecting rods 1 are each provided with a fixing piece;

[0045] The connecting rods 1 are each provided with two springs 11, and the support cavity structure of the converter is arranged between the two springs 11 on the same connecting rod 1.

[0046] Further, the axial compression structure further includes a screw nut 5 fixedly arranged on the lower top plate 2 close to the converter, and the screw nut 5 is threadedly engaged with the ball screw 7.

[0047] It should be noted that in the embodiments of the present disclosure, the axial compression structure has the functions of an axial energy consumption member and supporting the converter, and specifically, when subjected to a pulsation impact, the axial force generated by the deformation of the spring 11 sleeved on the connecting rod 1 is consumed, and at the same time, the screw nut 5 fixedly arranged on the lower top plate 2 is coaxial with the ball screw 7 and threadedly engaged with the ball screw 7, so that when the converter receives a pulsation impact, the ball screw 7 moves downward or upward, and at the same time, the ball screw 7 rotates due to the thread engagement, thereby converting the combined load into a radial force and consuming and eliminating the combined load.

[0048] It should be further noted that in some disclosed embodiments, the friction force between the screw nut 5 and the ball screw 7 is F f = μ α ZQ(1)

[0049] In the formula, Q is the contact load of the ball, μ α is the ball friction coefficient, and Z is the number of balls.

[0050] Wherein the contact load of the ball of the screw pair is:

[0051] In the formula, F a is the working load and the pre-tightening load of the screw pair, β is the contact angle, and λ is the helix angle.

[0052] Wherein the ball friction coefficient is:

[0053] In the formula, E is the elastic modulus of the screw pair material, is the surface quality coefficient, τ M is the shear strength of the node, τ L is the bonding shear strength of the lubricating film, δ S is the yield limit of the softer material in the contact pair, and δ is the contact stress.

[0054] Specifically, the friction torque between the screw nut 5 and the ball screw 7 is directly related to the pre-tightening force borne by the screw pair and the working load borne by the screw pair. The friction force borne by the screw pair can dissipate vibration energy, which is equivalent to a damping effect. The greater the pre-tightening force and the working load borne by the screw pair, the greater the friction force borne by the screw pair, and the better the energy dissipation effect. The better the structure is in reducing vibration.

[0055] Further, in the embodiment of the present disclosure, the total stiffness of the two springs 11 on the same connecting rod 1 is the same. It should be noted that the same stiffness of the two springs 11 means that they will produce similar deformation amounts when subjected to force, thereby maintaining the balance of the two ends of the connecting rod 1, reducing additional stress and vibration caused by stiffness differences. At the same time, in a dynamic environment, such as mechanical vibration or impact load, the combination of springs 11 with the same stiffness can better resist external interference and maintain the stable working state of the system. When the stiffness of the two springs 11 is the same, they can more evenly share the load acting on the connecting rod 1, avoid overloading of a single spring 11, prolong the service life of the spring 11, and the evenly distributed load helps to reduce stress concentration at the connecting part of the connecting rod 1 and the spring 11, reducing the risk of fatigue failure caused by stress concentration.

[0056] Preferably, as shown in FIGS. 2 and 3, two linear bearings 10 are fixedly arranged inside the support cavity structure, the linear bearings 10 are arranged on both sides of the angular contact ball bearing 9, and are respectively sleeved in the middle part of the axial compression structure.

[0057] Need to explain, the linear bearing 10 is used to support the guide of the cavity structure, reduce the friction when the support cavity structure moves on the connecting rod 1, improve the stability.

[0058] Preferably, in the embodiment of the present disclosure, a plurality of additional mass blocks 4 are detachably arranged inside the support cavity structure, and the plurality of additional mass blocks 4 are arranged symmetrically along the center of the support cavity structure; it should be noted that in the embodiment of the present disclosure, the support cavity structure includes two groups of bearing end covers 3 arranged at the upper and lower ends, a plurality of additional mass blocks 4 are arranged between the bearing end covers 3, the plurality of additional mass blocks 4 are arranged in the gap of the side wall of the ball screw 7 and the linear bearing 10, and the plurality of additional mass blocks 4 are arranged in the gap of the side wall of the ball screw 7 and the linear bearing 10. The plurality of additional mass blocks 4 can fix the relative position of the ball screw 7 and the linear bearing 10 on one hand, and can be used as counterweight on the other hand, so as to improve the working load.

[0059] Preferably, in the embodiment of the present disclosure, a limiting block is arranged at the top of the ball screw 7, and the bottom of the limiting block abuts against the top of the support cavity structure; it should be noted that in the embodiment of the present disclosure, the limiting block is a nut matched with the ball screw 7. Since the ball screw 7 is a variable-diameter structure, the top of the support cavity structure is fixed by screwing the matched nut, and the lower part of the support cavity structure abuts against the top of the variable-diameter section of the ball screw 7.

[0060] Preferably, the upper section of the ball screw 7 is a smooth shaft, and the lower section is a threaded shaft; it should be noted that in the embodiment of the present disclosure, the smooth shaft has a thread at the top, which is used for threaded connection of the matched nut for limiting, and an annular support ring is arranged between the smooth shaft and the threaded shaft, which is used for abutting against the upper support cavity structure.

[0061] Preferably, in the embodiment of the present disclosure, the energy-consuming flywheel 8 is fixedly connected to the bottom end of the ball screw 7 through a nut; in some embodiments, the bottom of the energy-consuming flywheel 8 is fixed to the bottom end of the ball screw 7 through two nuts, so as to improve the stability of the connection.

[0062] It should be noted that the present application relies on the ball screw pair to amplify the axial velocity of the shock absorber at both ends to the linear velocity of the rotation of the energy-consuming flywheel 8, uses the rotational inertia equivalent mass of the rotating energy-consuming flywheel 8, and adjusts the equivalent mass by increasing or decreasing the size and number of the energy-consuming flywheel 8. The adjustment is convenient, and the performance parameters of the damper can be quickly adjusted by adjusting the total stiffness of the spring 11 part, the lead of the ball screw pair, and the diameter and mass of the flywheel.

[0063] The embodiment also discloses a method of a variable-damping ball screw inertial damper, which comprises the following steps:

[0064] When the axial compression structure is subjected to the pulsating impact of the pipeline, the pulsating impact is transmitted downward to the converter, and the axial force is buffered and energy-dissipated by the deformation of the spring 11;

[0065] When the converter is subjected to the pulsating impact of the spring 11, the converter drives the ball screw 7 to move up and down along the axial direction and rotate, and the ball screw 7 rotates and dissipates energy in the process of rotation through the energy-dissipating flywheel 8.

[0066] Specifically, as shown in FIG. 4, FIG. 4 shows a force diagram of the inertia vibration damper under the action of the base excitation, and according to FIG. 4, the vibration control equation can be established as:

[0067] Wherein: z=x-y#(5)

[0068] In the formula, m is the main structure, is the second derivative of the main structure displacement, k is the spring stiffness, x is the main structure displacement, y is the base excitation displacement, is the first derivative of the base excitation displacement, F f is the friction force between the ball screws;

[0069] When the vibration system of the inertia vibration damper reaches a steady state, the mass m will generate a harmonic response with the same period but different phase as the excitation force. The period of the excitation force and the response is The maximum and minimum values of the harmonic response are in Within half a period, there is a phase difference between the harmonic response and the excitation force Within All

[0070] Assuming that the amplitude of the excitation force is

[0071] In the formula, Y is the amplitude of the base excitation displacement;

[0072] The boundary conditions are set as:

[0073] The displacement response of the equation of the boundary conditions is:

[0074] In the formula, is the frequency ratio, ω0 is the excitation force frequency, ω n The mass m is the natural frequency, is the damping function, is the friction function, and z0 is the main structure displacement response;

[0075] The work done by the equivalent viscous damping force in one vibration cycle is:

[0076] where A ep is the work done by the equivalent damping force, c ep is the equivalent damping coefficient;

[0077] The work done by the friction force in one cycle is:

[0078] where is the work done in one cycle;

[0079] The work done by the equivalent damping is equal to the work done by the dry friction, and the equivalent damping coefficient is:

[0080] The above shows and describes the basic principles and main features of the present application and the advantages of the present application, and it is obvious to those skilled in the art that the present application is not limited to the details of the above exemplary embodiments, and the present application can be implemented in other specific forms without departing from the spirit or essential characteristics of the present application. Therefore, the embodiments should be regarded as exemplary and non-limiting in any respect, and the scope of the present application is defined by the appended claims rather than the above description, and it is intended to encompass all variations falling within the meaning and scope of the equivalent elements of the claims. Any reference signs in the claims should not be regarded as limiting the claims involved.

[0081] Furthermore, it should be understood that although the present specification is described in terms of embodiments, not every embodiment contains only one independent technical solution, and the present specification is described in this way only for the sake of clarity, and those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that those skilled in the art can understand. The above is only to illustrate the technical idea of the present application, and cannot limit the protection scope of the present application, and any modification made on the basis of the technical solutions according to the present application falls within the protection scope of the claims of the present application.

Claims

1. A variable-damping ball-screw inerter shock absorber, characterized by, The axial compression structure is provided with a converter in the middle part of the axial compression structure, and the converter reciprocates along the axial direction in the axial compression structure by a spring (11); The converter comprises a support cavity structure, the middle part of the support cavity structure is fixedly provided with an angular contact ball bearing (9), the angular contact ball bearing (9) is coaxially provided with a ball screw (7), the upper section of the ball screw (7) is sleeved with the angular contact ball bearing (9), the lower section of the ball screw (7) is threadedly engaged with the axial compression structure, and the bottom end of the ball screw (7) is fixedly connected with an energy consumption flywheel (8).

2. The variable-damper ball screw inerter shock absorber of claim 1, wherein, The axial compression structure comprises an upper top plate (6) and a lower top plate (2), two parallel connecting rods (1) are provided between the upper top plate (6) and the lower top plate (2), and the connecting rods (1) are provided with fixing members at the ends. The connecting rods (1) are provided with two springs (11), and the support cavity structure of the converter is arranged between the two springs (11) on the same connecting rod (1).

3. The variable-damper ball-screw flywheel-accumulator shock absorber of claim 2, wherein, The axial compression structure further comprises a screw nut (5) fixedly arranged on the lower top plate (2) close to the converter, and the screw nut (5) is threadedly connected with the ball screw (7).

4. The variable-damper ball screw flywheel accumulator of claim 2, wherein, The total stiffness of the two springs (11) on the same connecting rod (1) is the same.

5. The variable-damper ball screw flywheel accumulator of claim 1, wherein, Two linear bearings (10) are fixedly arranged in the support cavity structure, the linear bearings (10) are arranged on both sides of the angular contact ball bearing (9) and are sleeved in the middle part of the axial compression structure.

6. The variable-damper ball screw flywheel accumulator of claim 1, wherein, A plurality of additional mass blocks (4) are detachably arranged in the support cavity structure, and the plurality of additional mass blocks (4) are symmetrically arranged along the center of the support cavity structure.

7. The variable-damper ball screw flywheel accumulator of claim 1, wherein, A limiting block is arranged at the top of the ball screw (7), and the bottom of the limiting block abuts against the top of the support cavity structure.

8. The variable-damper ball screw flywheel accumulator of claim 1, wherein, The upper section of the ball screw (7) is an optical axis, and the lower section is a threaded shaft.

9. The variable-damper ball screw flywheel accumulator of claim 1, wherein, The energy consumption flywheel (8) is fixedly connected to the bottom end of the ball screw (7) through a nut.

10. A method of a variable damping ball screw inerter shock absorber, characterized by, The variable damping ball screw inertial damper based on any one of claims 1-9 comprises the following steps: When the axial compression structure is subjected to a pipeline pulsation impact, the pulsation impact is transmitted downward to the converter, and the axial force is buffered and dissipated by the spring (11) through deformation; When the converter is subjected to the pulsation impact brought by the spring (11), the converter drives the ball screw (7) to move up and down along the axial direction and rotate, and the ball screw (7) rotates and dissipates energy through the energy consumption flywheel (8) in the process of rotation.

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