CN115949689A - Multi-degree-of-freedom damper for rod-shaped structure - Google Patents
Multi-degree-of-freedom damper for rod-shaped structure Download PDFInfo
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- CN115949689A CN115949689A CN202211606712.9A CN202211606712A CN115949689A CN 115949689 A CN115949689 A CN 115949689A CN 202211606712 A CN202211606712 A CN 202211606712A CN 115949689 A CN115949689 A CN 115949689A
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Abstract
The invention relates to a multi-degree-of-freedom damper for a rod-shaped structure, which comprises: the two end covers comprise cover bodies, elastic pieces and rotating connecting pieces; the elastic piece is arranged in the cover body, and the rotary connecting piece is connected in the elastic piece; the magnetic suspension bearings comprise stators and rotors; the stator is connected with the port of the cover body, and the rotor is positioned in the rotor; the rotor is provided with a magnetic part; and a mass block; the mass block is positioned between the rotors of the two magnetic suspension bearings, the mass block is coaxially connected with the rotors, and one end of the rotor far away from the mass block is rotatably connected with the elastic piece through a rotating connecting piece. The damper has high vibration suppression bandwidth, and can be suitable for low, medium and high frequency vibration suppression; and can suppress vibration with multiple degrees of freedom, thereby being suitable for multi-mode vibration.
Description
Technical Field
The invention relates to the technical field of vibration reduction, in particular to a multi-degree-of-freedom damper for a rod-shaped structure.
Background
The damper is mainly divided into an active form and a passive form. Passive dampers are classified into tuned, impulse, eddy current, electromagnetic, friction, and the like. The impact type, electromagnetic type, eddy type and friction type dampers have the characteristics of simple structure, wide damping frequency band and no need of tuning, and have the defect of low damping efficiency. The tuned damper has high single-frequency vibration reduction efficiency and has the defects of narrow vibration reduction bandwidth, large vibrator mass and poor robustness. Active dampers typically use the piezoelectric effect of crystals, by which a braking force is generated in a direction opposite to the structural vibration. The active damper has the defects of complex control program, poor suppression effect on unsteady vibration due to the convergence speed of the algorithm, low and medium-low frequency of the vibration suppression bandwidth, 2000Hz fundamental frequency of a high-speed electric spindle with the rotating speed of up to one hundred thousand revolutions and difficulty in meeting the requirements.
The rod-shaped structure with the large length-diameter ratio is multi-modal vibration and high-frequency modal vibration, but the rod-shaped structure is suitable for single-modal vibration or low-frequency modal vibration in the prior art. The prior art is therefore not suitable for large aspect ratio rod-like structures for multi-modal and high-frequency modal vibrations. It is necessary to design a high-frequency multi-degree-of-freedom damper, so as to be suitable for multi-mode vibration and a rod-shaped structure with a large length-diameter ratio of high-frequency modal vibration.
Disclosure of Invention
Therefore, the invention aims to solve the technical problem of overcoming the problem that the rod-shaped structure with large length-diameter ratio is not suitable for multi-mode vibration and high-frequency mode vibration due to the fact that the rod-shaped structure is suitable for single-mode vibration or low-frequency mode vibration in the prior art.
In order to solve the above technical problems, the present invention provides a multi-degree-of-freedom damper for a rod-shaped structure, comprising:
the two end covers comprise cover bodies, elastic pieces and rotating connecting pieces; the elastic piece is arranged in the cover body, and the rotary connecting piece is connected in the elastic piece;
the magnetic suspension bearings comprise stators and rotors; the stator is connected with the port of the cover body, and the rotor is positioned in the stator; the rotor is provided with a magnetic part;
and a mass block;
the mass block is positioned between the rotors of the two magnetic suspension bearings, the mass block is coaxially connected with one end of each rotor, and the other end of each rotor is rotatably connected with the elastic piece through the rotating connecting piece.
In some embodiments of the present invention, the rotor is provided with a mass cantilever and a connecting shaft at both ends thereof, the mass cantilever is connected with the mass block, and the connecting shaft is rotatably connected with the elastic member by a rotating connecting member. In some embodiments of the invention, the diameter of the mass cantilever is smaller than the diameter of the rotor, which is smaller than the diameter of the mass; and/or the presence of a gas in the atmosphere,
the diameter of the connecting shaft is smaller than that of the rotor.
In some embodiments of the invention, the magnetic member has an air gap with the stator of the magnetic bearing.
In some embodiments of the invention, the invention further comprises a housing, the housing is connected between the two magnetic bearings, and a ring is arranged; the shell is fixedly connected with the end cover.
In some embodiments of the present invention, the cover body is provided with a first clamping groove, a second clamping groove and a thread groove in sequence from outside to inside along the axis of the mass block; the elastic piece is clamped in the first clamping groove, and the stator of the magnetic suspension bearing is arranged in the second clamping groove;
the end face of the shell is pressed against the end face of the stator of the magnetic suspension bearing, and the shell is in threaded connection with the thread groove.
In some embodiments of the present invention, the rotational connector is a sliding bearing, the sliding bearing includes an outer ring and an inner ring, the outer ring is fixedly connected with the elastic member, and the inner ring is in rolling connection with the outer ring; and one end of the rotor, which is far away from the mass block, is connected with a connecting shaft, and the connecting shaft is fixedly connected with the inner ring.
In some embodiments of the invention, the stator is provided with a plurality of tooth grooves and a control part along the circumferential direction, a plurality of layers of first windings for generating radial electromagnetic induction and a plurality of layers of second windings for generating tangential electromagnetic induction are wound on the wall body of two adjacent tooth grooves, and the control part is electrically connected with the first windings and the second windings.
In some embodiments of the invention, the mass block is made of tungsten alloy or copper alloy; the cover body, the rotary connecting piece and the stator are made of light materials.
In some embodiments of the invention, the resilient member is a rubber gasket;
in the case of a high-speed state of the rotor: the rubber gasket is made of silicon-based rubber; in the case of a low-speed state of the rotor: the rubber gasket is made of polyurethane.
Compared with the prior art, the technical scheme of the invention has the following advantages:
the damper is provided with the mass block and the magnetic suspension bearing, when a stator of the magnetic suspension bearing is electrified, the magnetic suspension bearing supports the mass block and drives the rotor and the mass block to synchronously rotate, the torsional vibration is inhibited through the magnetic field tangential magnetic pull force of the magnetic suspension bearing, and the radial (transverse or longitudinal) vibration is inhibited through the radial magnetic pull force, so that the inhibition of multiple degrees of freedom is realized; in addition, under the state that the mass block rotates, the damper can be suitable for the vibration suppression of low, medium and high frequencies, and the damper can be subjected to frequency adjustment so as to suppress the vibration of different frequencies; secondly, this application is in the quiescent condition at the quality piece, and the quality piece is held up by rotation connecting piece and elastic component and is carried out the vibration energy of passive damping mode absorption to realize radial suppression. Therefore, the damper has high vibration suppression bandwidth, and is suitable for low, medium and high frequency vibration suppression; and can restrain vibration with multiple degrees of freedom, thereby being suitable for multi-mode vibration.
Drawings
In order that the manner in which the disclosure is made will be readily understood, a more particular description of the invention will be rendered by reference to specific embodiments thereof which are illustrated in the appended drawings
FIG. 1 is an exploded view of an inventive multiple degree of freedom damper for a rod-like structure;
FIG. 2 is an isometric view of a multiple degree of freedom damper for a rod-like structure of the invention;
FIG. 3 is a schematic view of the rotor of the multiple degree of freedom damper for a rod-like structure of FIG. 1;
FIG. 4 is a schematic diagram of a stator of the multiple degree of freedom damper for a rod-like structure of FIG. 1;
FIG. 5 is a schematic analysis of the multiple degree of freedom damper for a rod-like structure of FIG. 1 in a first semi-active mode of operation;
FIG. 6 is a schematic analysis of the multiple degree of freedom damper for a rod-like structure of FIG. 1 in a second semi-active mode of operation;
FIG. 7 is a schematic analysis of the multiple degree of freedom damper for a rod-like structure of FIG. 1 in a second semi-active mode of operation;
fig. 8 is a schematic structural view of an end cap in the multiple degree of freedom damper for a rod-like structure of fig. 1.
The specification reference numbers indicate: 100. an end cap; 110. a cover body; 111. a first card slot; 112. a second card slot; 113. a thread groove; 120. an elastic member; 130. rotating the connecting piece;
200. a magnetic suspension bearing; 210. a stator; 211. a tooth socket; 220. a rotor; 221. a magnetic member; 222. a mass cantilever; 223. a connecting shaft; 230. an air gap;
300. a mass block;
400. a housing.
Detailed Description
The present invention is further described in connection with the following figures and the detailed description so that those skilled in the art may better understand the invention and practice it, but the examples are not intended to limit the invention.
Referring to fig. 1 to 4, the present invention provides a multiple degree of freedom damper for a rod-shaped structure, including:
two end caps 100, wherein the end caps 100 comprise a cap body 110, an elastic member 120 and a rotating connecting member 130; the elastic member 120 is provided in the cover body 110, and the rotation link 130 is coupled in the elastic member 120;
two magnetic bearings 200, the magnetic bearings 200 comprising a stator 210 and a rotor 220; the stator 210 is connected to a port of the cover 110, and the rotor 220 is located in the stator 210; the rotor 220 is provided with a magnetic member 221;
and a mass 300;
the mass 300 is located between the rotors 220 of the two magnetic bearings 200, the mass 300 is coaxially connected to one end of the rotor 220, and the other end of the rotor 220 is rotatably connected to the elastic member 120 through the rotating connection member 130.
The stator 210 is provided with a plurality of slots 211 and control members along the circumferential direction, a plurality of layers of first windings for generating radial electromagnetic induction and a plurality of layers of second windings for generating tangential electromagnetic induction are wound on the wall body of two adjacent slots 211, and the control members are electrically connected with the first windings and the second windings.
The control member can respectively supply currents in different directions and different magnitudes to the first winding and the second winding, so that the first winding generates radial electromagnetic induction and the second winding generates tangential electromagnetic induction, and the magnetic member 221 on the rotor 220 interacts with the radial electromagnetic induction and the tangential electromagnetic induction to form radial magnetic induction force and tangential magnetic induction force. Radial magnetic induction forces are used for the lifting of the mass 300 and tangential magnetic induction forces are used for the rotation of the mass 300, i.e. the torsional vibrations are suppressed by the radial magnetic induction forces and the transverse or longitudinal vibrations are suppressed by the tangential magnetic induction forces.
In the damper according to the present embodiment, which can provide a plurality of degrees of freedom (i.e., can suppress vibrations in a plurality of modes), three operation modes (a semi-active operation mode and a passive operation mode) of the damper are described below:
1. semi-active mode of operation
In this mode, the magnetic suspension bearing 200 is powered on to support the mass 300 and drive the rotor 220 and the mass 300 to rotate synchronously, so that the magnetic field of the magnetic suspension bearing 200 suppresses the torsional vibration by tangential magnetic pull, and the radial magnetic pull suppresses the radial (transverse or longitudinal) vibration. The semi-active working mode is divided into a first semi-active working mode and a second semi-active working mode, and the principle analysis of the first semi-active working mode and the second semi-active working mode is as follows:
1.1 first semi-active operating mode (helix effect mode):
referring to fig. 5, the first half active operating mode is based on a helical effect of the rotor 220, the mass block 300 rotates around the z axis (i.e., a central axis of the mass block 300) at an angular velocity ω, a generated helical moment is L, vibration of an external structure generates disturbance to the rotating mass block 300 to generate an additional torque D, the rotor 220 generates a precession motion under the combined action of the helical moment L and the torque D, and a precession angle of the precession motion is an included angle between a resultant moment generated by the helical moment L and the torque D and the helical moment L, which is denoted as α; α = arctan (D/L). It can be seen from the formula that increasing the helical moment L can reduce the precession angle α, assuming the damper structure is symmetrical, the length of the damper mass 300 is 2d, the mass 300 precesses around its center of mass with the maximum amplitude d × tan (α), and the increasing helical moment L, α decreases, and the maximum amplitude decreases accordingly. The magnitude of the screw moment L is positively correlated with the rotation speed of the mass 300 and the mass of the mass 300. Therefore, the mass 300 is preferably a tungsten alloy or a copper alloy having a large specific gravity. Meanwhile, the mass block 300 is driven by the magnetic suspension bearing 200 to rotate at a high speed, the higher the rotating speed is, the larger the spiral moment L is, if the additional torque D is far smaller than L, according to a formula of α = arctan (D/L), α is a minimum value and is approximately 0, and any small disturbance does not have obvious influence on the structure amplitude. In other words, the first semi-active mode of operation achieves broadband vibration suppression. According to the Newton's third law, the mass 300 which moves stably transmits the acting force which is opposite to the external vibration outwards through the radial magnetic pulling force of the magnetic suspension bearing 200, and the external vibration is weakened. Therefore, the first semi-active operating mode of the present embodiment can be suppressed in a wide frequency range.
1.2 second semi-active mode of operation (rotor 220 tuned mode)
Referring to fig. 6, the second semi-active operation mode is based on the dynamic tuning principle of the spring vibrator unit composed of the rotor 220 and the mass 300, and according to the tuned damper principle, when the natural frequency of the rotor 220 and the mass 300 is consistent with the frequency of the forced vibration of the external structure, the energy of the forced vibration is transferred to the mass 300. Vibration energy can be dissipated by the eddy current effect of the mass 300 and the windings of the magnetic bearing stator 210.
This mode of operation mainly involves the prediction of the external forced vibration frequency (external disturbance frequency) and the prediction of the natural frequency of the spring vibrator unit composed of the mass 300 and the rotor 220. The forced vibration frequency or disturbance frequency is predicted by first placing the mass 300 in a stationary state or rotating at a constant speed. The external structure exciting force is transmitted to the air gap 230 through the cover 111 via the magnetic suspension bearing 200 stator 210, the air gap 230 is compressed by external disturbance, the air gap 230 is compressed to cause the magnetic flux change of the windings in the magnetic suspension bearing stator 210, the change of the winding magnetic flux generates high-frequency induced current in the stator windings, and the external forced vibration frequency or the disturbance frequency can be calculated according to the change direction of the high-frequency induced current. The frequency prediction process of the spring oscillator unit composed of the mass block 300 and the rotor 220 is as follows, when the natural frequency of the spring oscillator unit is close to the external excitation frequency, the external vibration energy is transferred to the spring array sub-unit, the amplitude of the spring oscillator unit reaches the local maximum value, and simultaneously the induced current of the magnetic suspension bearing winding also reaches the local maximum value. The rotational speed of the mass 300 may change the natural frequency of the spring vibrator unit, and the higher the rotational speed of the mass 300, the lower the natural frequency of the mass 300 (including the rotor 220 connected to the mass 300). In the semi-active mode, the corresponding high-frequency induced current peak value at the external disturbance frequency is monitored from the static slow acceleration mass block 300, and if the peak value of the high-frequency induced current is multiplied or obviously increased, the rotating speed is further increased, and the amplitude is reduced, the natural frequency of the spring vibrator unit at the moment can be judged to be close to the forced vibration or external disturbance frequency. By analogy, if the external forced vibration frequency or the disturbance frequency is more than one order, the amplitude of the induced current at the specified order frequency is only required to be monitored, the amplitude is multiplied, the rotating speed rising process is increased firstly and then reduced, and accordingly the natural frequency and the disturbance frequency of the spring oscillator unit can be judged to be close.
In the starting process of the damper, the magnetic suspension bearing 200 gradually increases the driving current, slowly increases the rotating speed of the mass block 300, and can reversely deduce the vibration amplitude of the rotor 220 through the change of the magnetic flux of the magnetic suspension bearing 200. The maximum vibration amplitude of the rotor 220 is the first-order natural frequency of the mass block 300, the second-order natural frequency of the second maximum vibration amplitude is the second-order natural frequency, and by analogy, the concerned frequency can be selected to be suppressed in the semi-active working mode two, that is, the damper can be frequency-modulated in the mode, so that different frequencies of an external structure are suppressed.
2. Passive mode of operation (Passive vibration suppression mode)
In this mode, the magnetic suspension bearing 200 is powered off, and the mass 300 is in a static state, so that the mass 300 is supported by the rotating connecting member 130 and the elastic member 120, and absorbs vibration energy in a passive vibration damping manner, thereby achieving a vibration damping effect. Meanwhile, the mass block 300 is axially and radially limited by the rotary connecting member 130, so that the mass block 300 is prevented from colliding with the housing 400. The specific principle analysis is as follows:
referring to fig. 7, the passive operation mode is based on the two-degree-of-freedom dynamic vibration absorber principle. The kinetic model can be simplified as shown in the following figure. F is the simple harmonic force applied to the main structure (the main structure comprises the external structure, the end cover 100, the shell 400, the stator 210 and other parts fixedly connected with the external structure); x is the number of d Displacement of the mass 300; theta d Is the torsion angle of the mass 300; m is a unit of 0 Mass of the primary structure; m is d Is the equivalent mass of the mass 300 and the rotor 220; k is a radical of i 、c i (i =1, 2) the stiffness, respectively the damping, of the elastic member 120; j of moment of inertia of mass 300 d Is (J) d ＝m d ρ) is the density of the proof mass 300; d 1 、d 2 Respectively, the distance from the supporting point of the two spring-damper units (i.e., the two elastic members 120) to the center of mass of the damper. When the magnetic suspension bearing 200 is not powered, the main structure vibration is transmitted to the mass 300 through the elastic member 120 and the rotating connection member 130. The vibration of the external structure is dissipated by the spring damping effect of the elastic member 120. It follows that the passive vibration suppression mode is capable of absorbing two-degree-of-freedom vibrations (i.e. radial suppression, the radial suppression being either lateral or longitudinal vibrations) and the frequency of the absorbed vibrations is close to the main structure vibration frequency.
Specifically, in the mass block 300 and the magnetic suspension bearing 200 provided in this embodiment, after the stator 210 of the magnetic suspension bearing 200 is energized, the magnetic suspension bearing 200 supports the mass block 300 and drives the rotor 220 and the mass block 300 to rotate synchronously, so that the torsional vibration is suppressed by the magnetic field tangential magnetic pull force of the magnetic suspension bearing 200, and the radial (lateral or longitudinal) vibration is suppressed by the radial magnetic pull force, thereby achieving suppression of multiple degrees of freedom; in addition, in the state that the mass block 300 rotates, the damper can be suitable for the vibration suppression of low, medium and high frequencies, and the damper can be subjected to frequency adjustment so as to suppress the vibration of different frequencies; secondly, in the present application, when the mass block 300 is in a static state, the mass block 300 is lifted by the rotating connection member 130 and the elastic member 120 to perform a passive vibration damping manner to absorb vibration energy, thereby achieving radial damping. Therefore, the damper has high vibration suppression bandwidth, and can be suitable for low, medium and high frequency vibration suppression; and can restrain vibration with multiple degrees of freedom, thereby being suitable for multi-mode vibration.
It should be noted that the damper is mainly applied to vibration suppression of a rod-shaped structure with a large length-diameter ratio. If the stirring rod is applied to a laboratory stirring rod with high length-diameter ratio, the shaking in the stirring process is reduced; the device is applied to a signal base station mounting rod to reduce wind-induced vibration; the suspension arm is applied to a gyroplane suspension arm, and the hovering stability is improved; the method is used for manufacturing the cutter rod with the large length-diameter ratio in the field of machining, inhibiting the shaking in the machining process and reducing the surface roughness of the machined part.
In addition, the damper has the advantages of low mass, high vibration suppression bandwidth, high single-frequency vibration suppression capability and the like.
Further, the rotor 220 is provided at both ends thereof with a mass cantilever 222 and a connecting shaft 223, respectively, the mass cantilever 222 is connected with the mass block 300, and the connecting shaft 223 is rotatably connected with the elastic member 120 through the rotating connection member 130. The mass cantilever 222 is made of tool steel, which has good toughness.
Further, the diameter of the mass cantilever 222 is smaller than the diameter of the rotor 220, and the diameter of the rotor 220 is smaller than the diameter of the mass 300.
Specifically, the mass cantilever 222 has a smaller diameter than the rotor 220 and the mass 300, such that the mass cantilever 222 separates the mass 300 from the rotor 220, thereby reducing the length of the rotor 220 and acting as a magnetic shield.
Further, the diameter of the coupling shaft 223 is smaller than that of the rotor 220.
Specifically, the diameter of the coupling shaft 223 is smaller than that of the rotor 220, and the coupling shaft 223 also plays a role of magnetic isolation.
Further, the diameter of the mass cantilever 222 is smaller than the diameter of the rotor 220, and the diameter of the rotor 220 is smaller than the diameter of the mass 300. The diameter of the coupling shaft 223 is smaller than that of the rotor 220.
Further, an air gap 230 is provided between the magnetic member 221 and the stator 210 of the magnetic bearing 200. The air gap 230 may be 0.5 to 2mm. Specifically, the air gap 230 between the magnetic member 221 and the stator 210 prevents the mass 300 from colliding with the inner wall of the housing 400 and prevents the inner wall of the housing 400 from interfering with the movement of the mass 300.
Further, the invention also comprises a shell 400, wherein the shell 400 is connected between the two magnetic suspension bearings 200 and is provided with a circle; the housing 400 is fixedly coupled to the end cap 100.
Specifically, a housing 400 is provided in this embodiment, and is connected to an external mechanism so that the vibration of the external mechanism is transmitted to the present damper through the housing 400; in addition, the housing 400 and the end cap 100 enclose the mass 300 therein, thereby preventing external factors from affecting the rotation of the mass 300.
As shown in fig. 8, further, the cover body 110 is provided with a first locking groove 111, a second locking groove 112 and a threaded groove 113 in sequence from outside to inside along the axis of the mass block 300; the elastic element 120 is clamped in the first clamping groove 111, the stator 210 of the magnetic suspension bearing 200 is installed in the second clamping groove 112, and the stator 210 is assembled in the second clamping groove 112 through interference fit;
the end face of the housing 400 abuts against the end face of the stator 210 of the magnetic bearing 200, and the housing 400 is screwed into the screw groove 113. The second engaging groove 112 and the threaded groove 113 have the same inner diameter.
Specifically, the present embodiment shows a connection manner of the cover 110, the elastic member 120, the stator 210 and the housing 400.
Further, the mass 300 has a cylindrical structure, and the mass 300 is integrally formed with the rotor 220 or connected by assembling.
Further, the rotating connecting piece 130 is a sliding bearing, the sliding bearing includes an outer ring and an inner ring, the outer ring is fixedly connected with the elastic piece 120, the elastic piece 120 is provided with a mounting groove, the outer ring is clamped in the mounting groove, and the inner ring is in rolling connection with the outer ring; one end of the rotor 220 far away from the mass block 300 is connected with a connecting shaft 223, and the connecting shaft 223 is fixedly connected with the inner ring.
Further, the mass block 300 is made of tungsten alloy or copper alloy; the cover 110 is made of a light material, and the housing 400 is also made of a light material, such as aluminum, so that the specific gravity of the mass 300 in the whole damper is increased, and the load of an external structure is reduced. The rotating connection 130 is made of a sliding bearing alloy, and the stator 210 is made of laminated silicon steel with low magnetic resistance.
Further, the elastic member 120 is a rubber gasket; in the case where the rotor 220 is in the high rotation state: the rubber gasket is made of silicon-based rubber, the heat resistance of the silicon-based rubber is good, and the rotor 220 is easy to generate heat when working at a high rotating speed, so that the rubber gasket is made of the silicon-based rubber with good heat resistance; in the case where the rotor 220 is in the low rotation state: the rubber gasket is made of polyurethane.
Further, the magnetic member 221 is of a ru-fe-b system.
Further, the stator 210 and the rotor 220 are provided with a reasonable number of pole slots so as to improve the operation efficiency of the magnetic bearing 200.
It should be understood that the above examples are only for clarity of illustration and are not intended to limit the embodiments. Other variations and modifications will be apparent to persons skilled in the art in light of the above description. And are neither required nor exhaustive of all embodiments. And obvious variations or modifications can be made without departing from the scope of the invention.
Claims (10)
1. A multi-degree-of-freedom damper for rod-shaped structures is characterized in that: the method comprises the following steps:
the two end covers comprise cover bodies, elastic pieces and rotating connecting pieces; the elastic piece is arranged in the cover body, and the rotary connecting piece is connected in the elastic piece;
the magnetic suspension bearing comprises a stator and a rotor; the stator is connected to a port of the cover body, and the rotor is positioned in the stator; the rotor is provided with a magnetic part;
and a mass block;
the mass block is positioned between the rotors of the two magnetic suspension bearings, the mass block is coaxially connected with one end of each rotor, and the other end of each rotor is rotatably connected with the elastic piece through the rotating connecting piece.
2. The multiple degree of freedom damper for a rod-like structure of claim 1, wherein: the two ends of the rotor are respectively provided with a mass cantilever and a connecting shaft, the mass cantilever is connected with the mass block, and the connecting shaft is connected with the elastic piece in a rotating mode through the rotating connecting piece.
3. The multiple degree of freedom damper for a rod-like structure of claim 2, wherein: the diameter of the mass cantilever is smaller than that of the rotor, and the diameter of the rotor is smaller than that of the mass block; and/or the presence of a gas in the gas,
the diameter of the connecting shaft is smaller than that of the rotor.
4. The multiple degree of freedom damper for a rod-like structure according to any one of claims 1 to 3, characterized in that: an air gap is arranged between the magnetic piece and the stator of the magnetic suspension bearing.
5. The multiple degree of freedom damper for a rod-like structure of claim 1, wherein: the magnetic suspension bearing is characterized by also comprising a shell, wherein the shell is connected between the two magnetic suspension bearings and is provided with a circle; the shell is fixedly connected with the end cover.
6. The multiple degree of freedom damper for a rod-like structure of claim 5, wherein: the cover body is provided with a first clamping groove, a second clamping groove and a thread groove from outside to inside in sequence along the axis of the mass block; the elastic piece is clamped in the first clamping groove, and the stator of the magnetic suspension bearing is arranged in the second clamping groove;
the end face of the shell is abutted against the end face of the stator of the magnetic suspension bearing, and the shell is in threaded connection with the thread groove.
7. The multiple degree of freedom damper for a rod-like structure of claim 1, wherein: the rotary connecting piece is a sliding bearing, the sliding bearing comprises an outer ring and an inner ring, the outer ring is fixedly connected with the elastic piece, and the inner ring is in rolling connection with the outer ring; and one end of the rotor, which is far away from the mass block, is connected with a connecting shaft, and the connecting shaft is fixedly connected with the inner ring.
8. The multiple degree of freedom damper for a rod-like structure of claim 1, wherein: the stator is provided with a plurality of tooth grooves and a control piece along the circumferential direction, a plurality of layers of first windings for generating radial electromagnetic induction and a plurality of layers of second windings for generating tangential electromagnetic induction are wound on the wall bodies of two adjacent tooth grooves, and the control piece is electrically connected with the first windings and the second windings.
9. The multiple degree of freedom damper for a rod-like structure of claim 1, wherein: the mass block is made of tungsten alloy or copper alloy; the cover body, the rotating connecting piece and the stator are made of light materials.
10. The multiple degree of freedom damper for a rod-like structure of claim 1, wherein: the elastic part is a rubber gasket;
in the case where the rotor is in a high rotation speed state: the rubber gasket is made of silicon-based rubber; in the case where the rotor is in a low rotation state: the rubber gasket is made of polyurethane.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211606712.9A CN115949689A (en) | 2022-12-13 | 2022-12-13 | Multi-degree-of-freedom damper for rod-shaped structure |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211606712.9A CN115949689A (en) | 2022-12-13 | 2022-12-13 | Multi-degree-of-freedom damper for rod-shaped structure |
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| CN115949689A true CN115949689A (en) | 2023-04-11 |
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| CN202211606712.9A Pending CN115949689A (en) | 2022-12-13 | 2022-12-13 | Multi-degree-of-freedom damper for rod-shaped structure |
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| CN (1) | CN115949689A (en) |
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2022
- 2022-12-13 CN CN202211606712.9A patent/CN115949689A/en active Pending
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