CN114704589A - Local resonance type phononic crystal vibration reduction device and equipment - Google Patents
Local resonance type phononic crystal vibration reduction device and equipment Download PDFInfo
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- CN114704589A CN114704589A CN202210421694.0A CN202210421694A CN114704589A CN 114704589 A CN114704589 A CN 114704589A CN 202210421694 A CN202210421694 A CN 202210421694A CN 114704589 A CN114704589 A CN 114704589A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/03—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using magnetic or electromagnetic means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
Abstract
The invention relates to a local resonance type phononic crystal vibration damper and equipment, which comprise a frame body, wherein a phononic crystal is arranged in the frame body, a vibrator of the phononic crystal is provided with a mass center adjusting piece, the mass center adjusting piece is connected with a lifting mechanism arranged on the frame body, and the mass center position of the vibrator is adjusted through the mass center adjusting piece so as to realize the adjustment of a band gap of the phononic crystal.
Description
Technical Field
The invention relates to the technical field of vibration suppression, in particular to a local resonance type photonic crystal vibration reduction device and equipment.
Background
The statements herein merely provide background information related to the present disclosure and may not necessarily constitute prior art.
The phononic crystal is an artificial periodic structure, and can generate a band gap for preventing elastic wave from propagating, so that the phononic crystal has a good application prospect in the field of vibration reduction by virtue of the special physical characteristic. The elastic wave cannot propagate in a specific frequency range, which is the band gap of the phononic crystal. Phononic crystals can be classified into Bragg scattering type phononic crystals and local resonance type phononic crystals according to the band gap generation principle thereof. The band gap frequency of the Bragg scattering type phononic crystal is of the same order of magnitude as the lattice constant, and thus a large size is required in order to obtain a low frequency band gap. The local resonance type phononic crystal is a vibrator with concentrated mass in the structure, the vibration occurs when the excitation of external frequency reaches a certain frequency, the elastic wave and the vibrator are coupled with each other so as to block the propagation of the elastic wave, and the band gap frequency is not influenced by the size of the phononic crystal. Therefore, the photonic crystal has the characteristic of controlling large wavelength in a small size, so that the local resonance type photonic crystal has a wider application prospect in low-frequency vibration suppression.
The traditional phononic crystal is designed only aiming at a single working condition or a special frequency band range, and is difficult to work under a complex working condition, particularly different frequency band vibration generated when the working condition changes, and at the moment, if the band gap range of the traditional phononic crystal is exceeded, an ideal vibration suppression effect cannot be achieved. The inventor finds that aiming at the problem, at present, two methods are mainly used for designing the band gap adjustable phononic crystal, and the adjustment of the band gap is realized by changing the shape of the structural main body or the mass of the oscillator. In the first mode, the adjustable rigidity phononic crystal can be designed by applying external force by utilizing the superelasticity of the material, so that the adjustment of the band gap is realized, however, as the external force is applied to the phononic crystal, the material can generate fatigue damage or even fracture along with the increase of the adjustment times, and the factors can influence the vibration reduction effect, so that the adjustment times and the adjustment range of the band gap are limited. The other is that the research on the mass change of the oscillator mainly realizes the increase and decrease of the mass of the oscillator through external excitation, at the moment, a weight-increasing material needs to be injected into or discharged from the oscillator to realize the adjustment of the mass of the oscillator, and an external driving device needs to be additionally arranged to supply the weight-increasing material, so that the complexity of the system is increased, the volume is increased, and the exertion of the advantage of controlling the large wavelength of the small size of the local resonance type photonic crystal is limited.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provides a local resonance type photonic crystal vibration reduction device which is simple in system and free from limitation of band gap adjusting times and adjusting range.
In order to achieve the purpose, the invention adopts the following technical scheme
In a first aspect, an embodiment of the present invention provides a local resonance type photonic crystal vibration damping device, which includes a frame body, a photonic crystal is disposed inside the frame body, a vibrator of the photonic crystal is provided with a centroid adjusting member, the centroid adjusting member is connected to a lifting mechanism mounted on the frame body, and a centroid position of the vibrator is adjusted by the centroid adjusting member to realize adjustment of a photonic crystal band gap.
Optionally, the barycenter regulating part is including being located the inside first magnet of barycenter cavity, and the periphery of oscillator is equipped with the second magnet that produces the suction to first magnet, second magnet and oscillator clearance fit, and the second magnet is connected with elevating system.
Optionally, the second magnet is an annular magnet, the second magnet is sleeved on the periphery of the oscillator, and a set distance is formed between the inner side surface of the second magnet and the outer peripheral surface of the oscillator.
Optionally, the support body is a box structure with an open top, the phononic crystal is connected with the bottom plate or the side plate of the support body, and the lifting mechanism is installed at the top of the support body.
Optionally, the phononic crystal is composed of a plurality of phononic crystal unit cells, and adjacent phononic crystal unit cells are connected through at least one group of bending beams;
further, the two bending beams of the same group are bent in opposite directions.
Optionally, the phononic crystal unit cell comprises a base frame, and the base frame is connected with the vibrator through at least one group of bending beams;
furthermore, a plurality of groups of bending beams are symmetrically arranged relative to the center of the base frame;
further, the two bending beams of the same group are bent in opposite directions.
Optionally, elevating system includes the magnet support, magnet support and second magnet fixed connection, magnet support top and regulating spindle threaded connection, and the regulating spindle rotates with the limiting plate of fixing at the support body top to be connected, and the limiting plate bottom surface is provided with the deflector, deflector and magnet support sliding connection.
Optionally, an annular boss is arranged on the axial surface of the adjusting shaft, the top surface of the annular boss contacts with the bottom surface of the limiting plate, and the bottom surface of the annular boss is used for limiting the highest height of the magnet support.
Optionally, the top of the adjusting shaft is fixedly connected with the rotating handle;
furthermore, the top end of the adjusting shaft is fixedly connected with the rotating handle through a locking piece, and the adjusting shaft is matched with the rotating handle through a square insertion block and a square slot.
In a second aspect, embodiments of the present invention provide an apparatus provided with a local resonance type photonic crystal vibration damping device as described in the first aspect.
The invention has the beneficial effects that:
1. according to the vibration damper, the vibrator is provided with the mass center adjusting piece, the position of the mass center can be adjusted through the lifting mechanism, compared with the existing mode of changing the structural shape of the main body of the vibrator, external force does not need to be applied to the vibrator, materials cannot be subjected to fatigue damage or even fracture along with the increase of the adjusting times, and further the adjusting times and the adjusting range of the band gap cannot be influenced.
2. Compared with the existing mode of adjusting the mass of the oscillator, the oscillator of the vibration damper can be directly arranged on the frame body without arranging an additional weight-increasing material supply system, simplifies the vibration damping system and is beneficial to the exertion of the advantage of controlling the large wavelength of the local resonance type photonic crystal in a small size.
3. According to the vibration damper, the adjacent phononic crystal unit cells are connected through the multiple groups of bending beams, the base frame of the phononic crystal unit cells is connected with the vibrator through the multiple groups of bending beams, the bending beams are low in rigidity, a low-frequency band gap can be generated, bottom frequency vibration damping is achieved, and the vibration damping effect of the whole vibration damper is enhanced.
4. The vibration damper drives the first magnet to move through the second magnet, so that the mass center of the vibrator is adjusted, the mass center adjusting part is simple and convenient to assemble and assemble, and the second magnet is of an annular structure, so that the attraction force of the second magnet to the first magnet is ensured, and the movement of the first magnet is further ensured.
5. According to the damping device, in the lifting mechanism, the top of the magnet support is in threaded connection with the adjusting shaft, the lifting movement of the magnet support is adjusted through threads, the adjusting precision is high, and the requirement of a required band gap is met.
6. According to the vibration damper, the adjusting shaft is matched with the rotating handle through the square insertion block and the square insertion groove, so that the rotating handle and the adjusting shaft are prevented from being rubbed to reduce the rotating precision in the long-term use process.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the application and, together with the description, serve to explain the application and are not intended to limit the application.
FIG. 1 is an external view of the overall structure of embodiment 1 of the present invention;
FIG. 2 is an internal view of the overall structure of embodiment 1 of the present invention;
FIG. 3 is a sectional view showing the whole structure of embodiment 1 of the present invention;
FIG. 4 is a schematic diagram of the phononic crystal structure of example 1 of the present invention;
FIG. 5 is a schematic diagram of a phononic crystal unit cell structure in example 1 of the present invention;
FIG. 6 is a schematic structural view of a lifting mechanism in embodiment 1 of the present invention;
fig. 7 is a schematic view of the lifting mechanism and a second magnet according to embodiment 1 of the present invention;
FIG. 8 is a schematic view of a magnet holder according to embodiment 1 of the present invention;
FIG. 9 is a schematic view showing the assembly of the turning handle and the adjusting shaft in embodiment 1 of the present invention;
FIG. 10 is a schematic diagram of the principle of adjusting the center of mass of the vibrator in embodiment 1 of the present invention;
FIG. 11 is a band diagram of a first magnet spaced 0mm from the upper surface of a cylindrical structure according to example 1 of the present invention;
FIG. 12 is an energy band diagram of a first magnet at a distance of 12.5mm from the upper surface of a cylindrical structure according to example 1 of the present invention;
FIG. 13 is a mode diagram of example 1 of the present invention in which the first magnet is spaced apart from the upper surface of the cylindrical structure by 0mm and 12.5 mm;
FIG. 14 is graphs showing transmission characteristics of a first magnet of example 1 of the present invention at 0mm and 12.5mm from the upper surface of a cylindrical structure;
FIG. 15 is a graph showing the variation of the band gap characteristic of the phononic crystal according to the distance from the first magnet to the upper surface of the cylindrical structure in example 1 of the present invention;
FIG. 16 is a graph showing the variation of the band gap width of the phononic crystal according to the distance from the first magnet to the upper surface of the cylindrical structure in example 1 of the present invention;
the device comprises a base plate 1, a first side plate 2, a second side plate 3, a fixing plate 4, a counter bore 5, a bending beam 6, a base frame 7, a base 8, a cylindrical structure 9, a first magnet 10, a second magnet 11, a limiting plate 12, a guide plate 13, a M1.6 screw 14, a placing cylinder 15, an annular table 16, an inverted U-shaped plate 17, an external thread shaft section 18, a smooth shaft section 19, an annular boss 20, a rotating handle 21, a bolt 22, an M2, a side plate 23 and an insert 24.
Detailed Description
Example 1
The present embodiment provides a local resonance phononic crystal vibration damping device, as shown in fig. 1 to 3, which includes a phononic crystal, where the phononic crystal includes a vibrator with concentrated mass, and resonates when excitation of external frequency reaches a certain frequency, and an elastic wave is coupled with the vibrator to block propagation of the elastic wave, so as to perform a vibration suppression function.
The local resonance phononic crystal vibration damping device of this embodiment includes support body, phononic crystal, barycenter regulating part and elevating system, and the phononic crystal is installed on the support body, and the support body is used for being connected with the equipment of treating the damping, and elevating system drives the barycenter regulating part and is the elevating movement, and then makes the barycenter of phononic crystal change, reaches the purpose that the band gap was adjusted.
Specifically, the support body adopts the box structure of being made by rigid material, and the open setting in top of box structure, because the damping characteristic of phononic crystal, its rigidity is lower, consequently the support body provides certain rigid support for the phononic crystal and prevents that it from losing the damping function when bearing.
The box structure includes bottom plate 1, and two longer edges of bottom plate 1 are fixed with bottom plate 1 vertically first curb plate 2, and two 1 shorter edges of bottom plate are fixed with bottom plate 1 vertically second curb plate 3, first curb plate 2 and 3 mutually perpendicular of second curb plate, and bottom plate 1, two first curb plates 2 and two second curb plates 3 constitute the box structure of the uncovered setting in top jointly.
The bottom of the outer side face of the second side plate 3 is provided with a fixing plate 4, and the fixing plate 4 is provided with a counter bore 5 for fixing the whole frame body and the equipment to be damped.
In order to ensure the fixing strength between the vibration damping device and the equipment, the fixing plate is provided with a plurality of counter bores 5, in this embodiment, the fixing plate is provided with two counter bores 5, and the vibration damping device and the equipment can be fixed through the bolts and the counter bores 5.
It will be appreciated that the fixing plate 5 may also be provided at the bottom of the first side plate 2, depending on the actual situation of the device to be damped.
The phononic crystal is arranged inside the frame body, is connected with the frame body and can receive vibration excitation generated by the outside transmitted by the frame body.
As shown in fig. 4-5, the phononic crystal is formed by arranging a plurality of phononic crystal unit cells along the length direction of the first side plate 2, and is arranged at the bottom of the frame body, the number of the phononic crystal unit cells can be set according to actual needs, and is related to the size of the box body and the size of the equipment to be damped.
The single phonon crystal cell comprises a base frame 7, the base frame 7 in the embodiment is a rectangular frame or a circular frame or a square frame, for convenience, adjacent phonon crystal cells are connected through bending beams 6, the base frame 7 is a square frame and is provided with four frames with equal length, the adjacent phonon crystal cells are mutually close to the frames and are connected through two groups of bending beams 6, the same group of the frames is provided with two bending beams 6, and the bending directions of the two bending beams 6 are opposite.
Specifically, a first group of bending beams between adjacent phononic crystal unit cells are a first bending beam and a second bending beam which are distributed from one end part of the frame to the middle part, the first bending beam bends towards the middle part of the frame, the bending direction of the second bending beam is opposite to that of the first bending beam, a second group of bending beams are a third bending beam which is close to the second bending beam and a fourth bending beam which is arranged at the other end part of the frame, the fourth bending beam bends towards the middle part of the frame, and the bending direction of the third bending beam is opposite to that of the fourth bending beam.
The oscillator is arranged in the inner space of the base frame 7 and comprises a base 8, the base 8 is of a cuboid structure, the upper surface of the base is provided with a tubular structure 9, the tubular structure 9 can be a cylindrical tube or a square tube, and the tubular structure in the embodiment is a cylindrical tube.
The base 8 is connected with the base frame 7 through at least one group of bending beams 6, and the plurality of groups of bending beams 6 are symmetrically arranged relative to the center of the base 8.
Specifically, two sides that are parallel to the phononic crystal unit cell arrangement direction in the base 8 are connected with the frame that is parallel to the phononic crystal unit cell arrangement direction through the bending beam 6, and in this embodiment, a set of bending beams is provided between the side of the base 8 and the corresponding frame, and the same set of bending beams are all bent towards the direction in the middle of the base.
The bending beam has lower rigidity, can generate low-frequency band gap, realizes bottom frequency vibration reduction, and enhances the vibration suppression effect of the whole vibration reduction device.
The bending beam 6 between the adjacent phononic crystal unit cells can restrain the vibration along the length direction of the first side plate 2, and the bending beam 6 between the base 8 and the frame of the vibrator can damp the vibration along the length direction of the first side plate 2, so that the vibration restraining effect is enhanced.
The phononic crystal is connected with the bottom plate 1 or the side plate of the frame body, the bottom of the phononic crystal is connected with the bottom of the second side plate 3 of the frame body through two groups of bending beams 6 in the embodiment, the bending beams 6 arranged between adjacent phononic crystal unit cells are arranged in the same mode, and the difference is that the bending beam 6 at the position is of a quarter-circle structure. And the bending beam 6 at the position is supported by the step structure between the bottom plate 1 and the second side plate 3, so that the two step structures support the phononic crystal from two ends of the phononic crystal, and the stability of the phononic crystal and the installation of the support body is guaranteed.
In the embodiment, the cross section of the curved beam 6 is a semicircular beam with the width of 0.4mm, the radius of 4.25mm, the distance between the circle centers of 18.40mm and the height of 5 mm; the size of a base frame 7 of the square of the phonon crystal unit cell is 40mm, the height of the base frame is 5mm, the diameter of an outer circle of a cylindrical structure 9 is 18.4mm, the diameter of an inner circle of the cylindrical structure 9 is 17mm, the height of an inner cavity of the cylindrical structure 9 is 24.5mm, the height of an outer part of the cylindrical structure is 25mm, the side length of a base 8 is 18.4mm, and the height of the base is 5 mm.
The material selection of the phononic crystal is AlSi10Mg material, and the parameters are as follows: density rho 2750kg/m3The modulus of elasticity E is 69.85GPa, and the Poisson ratio is 0.33.
It is understood that the sizes and materials of the bending beam 6 and the phononic crystal can be set by those skilled in the art according to actual needs.
The vibrator is used as a part for concentrating the mass of the photonic crystal, the traditional mode for changing the band gap is realized by changing the shape of the main structure of the photonic crystal or the mass of the vibrator, when the shape of the main structure of the photonic crystal is changed, external force needs to be applied to the photonic crystal, for example, a set value of torque needs to be applied to the main structure of the photonic crystal, so that the shape of the main structure of the photonic crystal is deformed, however, by adopting the mode, after multiple band gap adjustments, the main structure of the photonic crystal is easily subjected to fatigue damage and even fracture, and the adjustment range of the band gap is limited due to the limitation of the deformation degree, when the mass of the vibrator is changed, a weight increasing material needs to be injected into the cylindrical structure, for example, water is introduced, at the moment, a pump body and a water source need to be additionally arranged, so that the complexity of the whole system is increased, therefore, in the embodiment, the vibrator has a mass center adjusting part, the natural frequency of the vibrator is changed by adjusting the mass center of the vibrator, so that the adjustment of the band gap is realized, external force is not required to be applied to the vibrator, other equipment is not required to be additionally arranged, the system is simplified, and the advantage of controlling the large wavelength by the small size of the local resonance type photonic crystal is played.
Specifically, the centroid adjusting piece comprises a first magnet 10 located inside the tubular structure, and the outer peripheral surface of the first magnet 10 is attached to the inner side surface of the tubular structure 9 and is in sliding connection with the inner side surface of the tubular structure 9.
The height of the first magnet 10 is smaller than that of the cavity in the tubular structure 9, so that the first magnet 10 has a space in the cavity for moving along the axis of the tubular structure 9, the first magnet 10 is a mass concentration element as a part of the vibrator, and the mass center of the vibrator can be adjusted through the movement of the first magnet 10.
In this embodiment, the height of the first magnet 10 is 1/2 of the height of the inner cavity of the tubular structure 9, and in other embodiments, the height of the first magnet 10 may also be 1/3 or 1/4 of the height of the inner cavity of the tubular structure 9, which may be set according to actual needs.
The periphery of tubular structure 9 is provided with second magnet 11, and second magnet 11 can produce the suction to first magnet 10, and second magnet 11 is connected with elevating system, and elevating system can drive first magnet 10 through second magnet 11 and move along tubular structure 9's axis direction, and then realize the regulation of oscillator barycenter.
The second magnet 11 may be a cubic magnet disposed on one side of the tubular structure 9, and the cubic magnet has a gap with the tubular structure 9 to leave a space for the vibrator to generate vibration.
In another embodiment, the second magnet 11 is a ring magnet matched with the cylindrical structure 9, the second magnet 11 is sleeved on the outer periphery of the cylindrical structure 9 and is arranged coaxially with the cylindrical structure 9, and the second magnet 11 is in clearance fit with the cylindrical structure 9, that is, the inner side surface of the second magnet 11 and the outer side surface of the cylindrical structure 9 have a set gap so as to leave a space for generating vibration by the vibrator.
In this embodiment, the second magnet 11 is of an annular structure, which increases the area of the attraction force generated with the first magnet 10, so that the first magnet 10 receives sufficient attraction force, and can stably move along the axial direction of the tubular structure 9 without falling.
In a practical application, the first magnet 10 and the second magnet 11 are made of neodymium iron boron, and the parameters are as follows: density rho 7600kg/m3The elastic modulus E is 160GPa, and the Poisson ratio is 0.24.
Elevating system installs the top surface at the support body, because the uncovered setting of support body, consequently makes things convenient for user of service to operate elevating system and goes up and down second magnet 11, and then conveniently regulates and control the position of oscillator barycenter.
As shown in fig. 6-9, the lifting mechanism includes a magnet support, an adjusting shaft and a limiting plate 12, a second magnet 11 is placed on the magnet support, the limiting plate 12 is fixed on the top surface of the frame body, the adjusting shaft is coaxially arranged with the tubular structure, the adjusting shaft passes through the limiting plate and then is connected with the magnet support through threads, the adjusting shaft is rotatably connected with the limiting plate 12 and can move around the axis direction, the side surface of the magnet support is slidably connected with a guide plate 13 fixed on the bottom surface of the limiting plate 12, and the guide plate 13 is arranged to enable the magnet support to rotate along with the adjusting shaft and only move along the axis direction of the adjusting shaft.
Specifically, the limiting plate 12 is a strip plate, one end of the limiting plate 12 is fixed to the middle of the top surface of the second side plate 3 at one end of the rack body through the M1.6 screw 14, and the other end of the limiting plate 12 is fixed to the middle of the top surface of the second side plate 3 at the other end of the rack body through the M1.6 screw 14.
Magnet support includes that one places a section of thick bamboo 15 with second magnet shape assorted, places the uncovered setting in a 15 both ends, places a 15 bottom inner edge departments of section of thick bamboo and is provided with an annular platform 16, and second magnet 11 is placed at the upper surface of annular platform 16, and the internal diameter of annular platform is greater than tubular structure 9's external diameter to make magnet support can be smooth do elevating movement along tubular structure 9's axis.
The top surface of placing a section of thick bamboo 15 is provided with an inverted U template 17, and inverted U template 17 includes horizontal plate and the vertical plate that sets up at the horizontal plate tip, the one end of vertical plate and the tip fixed connection of horizontal plate, and the other end is fixed at the top surface of placing a section of thick bamboo. The central part of horizontal plate portion is provided with the screw hole, and horizontal plate portion passes through screw hole and regulating spindle threaded connection, and the screw hole in this embodiment is the M5 screw hole.
The adjusting shaft is provided with an external thread shaft section 18, and the adjusting shaft is in threaded connection with the horizontal plate part through the external thread shaft section 18.
The regulating shaft comprises an external thread section 18 and a light shaft section 19, the diameter of the light shaft section 19 is larger than the outer diameter of the external thread section 18, the external thread section 18 is rotatably connected with the magnet support, and the light shaft section 19 is rotatably connected with the limiting plate 12 through an opening formed in the limiting plate 12.
The outer surface of the optical axis section 19 is provided with an annular boss 20 to form a shaft shoulder structure, the upper surface of the annular boss 20 is in contact with the lower surface of the limiting plate 12, on one hand, the adjusting shaft can be prevented from being separated from the limiting plate 12, and on the other hand, the highest moving position of the magnet support is limited.
In other embodiments, the outer surface of the optical axis segment is provided with a plurality of limiting blocks which are arranged at equal intervals along the circumference so as to play the same role as the annular boss.
The top of regulating spindle is connected with twist grip 21, and the staff can drive the regulating spindle through twist grip 21 and rotate around self axis.
The rotating handle 21 in this embodiment is a rectangular parallelepiped block, and in other embodiments, the rotating handle 21 may also be a cross-shaped block, a cylindrical block, or a positive multi-variable block, which is convenient to operate.
In a preferred embodiment, the turning handle 21 is a regular hexagonal block or a regular pentagonal block, which facilitates the turning of the turning handle 21 by a worker using a wrench.
The rotating handle 21 is fixedly connected with the optical axis section 19 of the adjusting shaft through a bolt, in the embodiment, a countersunk hole is formed in the middle of the rotating handle 21, correspondingly, a threaded hole is formed in the top surface of the optical axis section 19, the bolt is fixedly connected with the optical axis section 19 through the countersunk hole and the threaded hole, the depth of the countersunk hole is larger than the thickness of the head of the bolt, the head of the bolt cannot protrude out of the upper surface of the rotating handle, and the whole vibration damping device is convenient to install and fix with the equipment to be damped.
The bolt in this embodiment is an M2 bolt 22, and it can be understood that a person skilled in the art can select a corresponding bolt to fix the adjusting shaft and the rotating handle 21 according to actual needs.
In this embodiment, each magnet holder is correspondingly provided with two guide plates 13, the guide plates 13 are fixed on the lower surface of the limiting plate 12, one of the guide plates 13 is in sliding fit with one second plate portion of the magnet holder, and the other guide plate 13 is in sliding fit with the other second plate portion of the magnet holder.
Through the setting of deflector 13 for when turning handle 21 drives the regulating spindle and rotates around self axis, the magnet support can not rotate around regulating spindle self axis, and only can follow the axis direction motion of regulating spindle, and then utilizes the adsorption affinity of second magnet 11 to adjust the position of first magnet 10 at the inside cavity of tubular structure 8.
In other embodiments, the guiding plate 13 can be matched with the second plate part of the magnet bracket in a sliding block and sliding groove mode, and the guiding effect is better.
Two sides of the first plate part of the magnet support, which are parallel to the arrangement direction of the single phonon crystal cells, are provided with side plates 23, and the side plates 23 can be in sliding fit with the side surfaces of the limiting plates 12, so that the magnet support can be further guided in motion.
In order to prevent friction between the turning handle and the adjusting shaft during long-term use and reduce the rotation precision, the top end surface of the adjusting shaft is matched with the turning handle 21 through a square slot and an inserting block 24.
Specifically, the top surface of the adjusting shaft is provided with a square insertion block 24, the horizontal section of the insertion block 24 can be square, rectangle or polygon, the polygon can be regular polygon or irregular polygon, the horizontal section of the insertion block 24 in the embodiment is square, and the side length of the square is 3 mm.
In another embodiment, the top surface of the adjusting shaft is provided with a slot, and the bottom surface of the rotating handle is provided with an insertion block, and the insertion block is inserted into the slot.
In this embodiment, drive the motion of first magnet 10 through second magnet 11, and then realize the regulation of oscillator barycenter, the barycenter regulating part is simple, convenient assembly and equipment, and elevating system adopts regulating spindle and magnet support, and simple easy operation can direct mount on the support body, need not to set up extra equipment, has guaranteed the simplification of whole device, is favorable to the performance of the advantage of the big wavelength of local resonance type phononic crystal small-size control.
Meanwhile, the lifting movement of the magnet support is realized in a thread matching mode, so that accurate adjustment can be realized, the adjustment precision is improved, and the requirement for meeting the required band gap is met.
The method for adjusting the band gap by the damping device in the embodiment comprises the following steps:
as shown in fig. 10, the staff manually rotates the rotating handle 21, and then drives the adjusting shaft to rotate around the axis of the staff, under the action of the guide plate 13, the magnet support is in lifting motion, because the second magnet 11 has adsorption force on the first magnet 10, therefore, under the action of the adsorption force, the first magnet 10 is driven to be in lifting motion in the tubular structure of the oscillator, so that the distance between the first magnet 10 and the upper surface of the tubular structure 9 changes, and then the mass center of the oscillator is adjusted, thereby the adjustment of the band gap is realized, and because each magnet support is mutually independent, the mass center of the oscillator of each phononic crystal unit cell can be independently adjusted.
The damping device of this embodiment is based on the local resonance mechanism, and the damping main part is phononic crystal, adopts annular second magnet to utilize elevating system to drive, realizes the adjustable function of band gap. The damping device can generate a low-frequency band gap, the height of the first magnet in the cavity in the vibrator is adjusted, the frequency range of the band gap can be actively adjusted according to actual production scenes, and therefore the damping device has a very good damping effect on low-frequency vibration. The vibration damping device of the embodiment can be directly installed in equipment with vibration suppression requirements, and the movement of the internal magnet is realized through the control of the adjusting handle, so that the suppression of the vibration with special frequency under the required working condition is realized.
The band gap adjustment of the damping device of the present embodiment is simulated by the finite element method as follows:
in this embodiment, simulation analysis was performed using a solid mechanics module in COMSOL Multiphysics 5.6 software. In the solid mechanics module, a geometric model of a phononic crystal unit cell is established as shown in fig. 5, the material parameters are input, Floquet-Bloch periodic boundary conditions are set, grid division is carried out on the geometric model, and frequency sweeping is carried out on Bloch wave vector kx in a first irreducible Brillouin zone, so that an energy band diagram of the phononic crystal can be obtained. The frequency range through which a mode of the band diagram without any elastic wave passes is the band gap of the phononic crystal. In the case of only changing the height of the inner magnet, the above process is repeated to determine the influence of different magnet heights on the band gap and to determine the band gap adjustable range of the phononic crystal 1, and the distance of the inner first magnet from the upper surface of the cylindrical structure is defined in the manner shown in fig. 10.
As can be seen from FIG. 11, the band gap of the inner first magnet is 337.39Hz-733.54Hz when the distance from the upper surface is 0 mm. As can be seen from FIG. 12, the band gap of the inner first magnet is 407.77Hz-941.8Hz when the distance from the upper surface is 12.5 mm.
From the modal analysis of fig. 13, it is understood that in both limit states, the oscillator resonates under external excitation, and in both of these modes, energy is concentrated in the oscillator, and the frame does not vibrate, and at this time, vibration cannot propagate, and therefore a band gap occurs. At the upper boundary of the band gap, the vibration of the vibrator is reduced at this frequency, and the frame starts to vibrate, and at this time, the vibration can propagate through the phonon crystal, so that the band gap is stopped.
The phononic crystal provided by the embodiment can generate a wide-frequency band gap, and in order to determine the vibration damping performance, the transmission characteristic of the phononic crystal needs to be analyzed.
Finite element analysis is carried out by using COMSOL Multiphysics 5.6 software, firstly establishing a geometrical model of the phononic crystal in the software, setting a perfect matching layer to reduce the influence of wave reflection on the transmission characteristic of the phononic crystal, applying a displacement of 0.001m in the x direction on the left side of the phononic crystal, and carrying out frequency sweep of 1Hz-1000HzAnd the right side of the phononic crystal is provided with a collecting surface, so that input and output displacement signals under different frequencies are obtained. And finally, according to a transmission loss formula:
where TL is the transmission loss of the phononic crystal 1, PoutTo output a displacement signal, PinTo input a displacement signal.
The shaded part of fig. 14 shows that the transmission loss of the inner first magnet in the highest and lowest states is obviously different, the attenuation range is basically consistent with the band gap range of the energy band diagram, the band gap range is obviously changed under different heights, and the transmission loss is stabilized below-40 dB, which proves that the phononic crystal has good vibration suppression performance.
It can be seen from fig. 15 that the frequency of the lower band gap boundary rises from 337.39Hz to 405.21Hz as the height of the inner first magnet from the upper surface increases, and the frequency of the upper band gap boundary rises from 733.54Hz to 935.8Hz as the height of the inner first magnet from the upper surface increases. It can be seen from fig. 16 that the band gap width increases from 396.15Hz to 534.03Hz as the distance from the inner first magnet to the upper surface increases. It can be considered that the band gap frequency range is shifted toward high frequencies as the height of the inner first magnet from the upper surface increases, and the band gap width increases.
Example 2
The embodiment discloses equipment, wherein the local resonance phononic crystal vibration damping device in the embodiment 1 is arranged at a part needing vibration damping, the equipment is a machine tool or a vehicle and the like, and the part needing vibration damping is fixedly connected with the vibration damping device in the whole embodiment 1 through a counter bore 5 and a fixing bolt on a fixing plate 4. Other structures of the device can adopt the existing structures, and the specific structure of the device is not described in detail here.
It is understood that the local resonance phononic crystal vibration damping device described in embodiment 1 can be installed on the equipment needing vibration damping by those skilled in the art according to the actual needs.
Although the embodiments of the present invention have been described with reference to the accompanying drawings, it is not intended to limit the scope of the invention, and it should be understood by those skilled in the art that various modifications and variations can be made without inventive changes in the technical solutions of the present invention.
Claims (10)
1. The utility model provides a local resonance type phononic crystal vibration damper which characterized in that, includes the support body, and the support body is inside to be provided with the phononic crystal, and the oscillator of phononic crystal is provided with the barycenter regulating part, and the barycenter regulating part is connected with the elevating system who installs at the support body, adjusts the barycenter position of oscillator in order to realize the regulation of phononic crystal band gap through the barycenter regulating part.
2. The local resonance type photonic crystal vibration damping device according to claim 1, wherein said center of mass adjusting member comprises a first magnet located inside the center of mass cavity, and a second magnet generating an attraction force to the first magnet is provided on the outer periphery of the vibrator, the second magnet being in clearance fit with the vibrator, and the second magnet being connected to the elevating mechanism.
3. The local resonance type photonic crystal vibration damping device according to claim 2, wherein said second magnet is a ring magnet, and said second magnet is fitted around the outer periphery of the vibrator with its inner side surface spaced from the outer peripheral surface of the vibrator by a predetermined distance.
4. The local resonance type phononic crystal vibration damping device according to claim 1, wherein the frame body is a box structure with an open top, the phononic crystal is connected with a bottom plate or a side plate of the frame body, and the lifting mechanism is installed at the top of the frame body.
5. The local resonance type phononic crystal vibration damping device according to claim 1, wherein the phononic crystal is constituted by a plurality of phononic crystal cells, adjacent ones of which are connected by an upper set of bending beams;
further, the two bending beams of the same group are bent in opposite directions.
6. The local resonance type photonic crystal vibration damping device according to claim 5, wherein the photonic crystal unit cell comprises a base frame, the base frame being connected to the vibrator through at least one set of bending beams;
furthermore, a plurality of groups of bending beams are symmetrically arranged relative to the center of the base frame;
further, the two bending beams of the same group are bent in opposite directions.
7. The local resonance type photonic crystal vibration damper according to claim 1, wherein said elevating mechanism comprises a magnet holder, said magnet holder is fixedly connected to said second magnet, the top of said magnet holder is threadedly connected to said adjusting shaft, said adjusting shaft is rotatably connected to a position-limiting plate fixed to the top of said frame, a guide plate is disposed on the bottom surface of said position-limiting plate, and said guide plate is slidably connected to said magnet holder.
8. The local resonance type photonic crystal vibration damping device according to claim 7, wherein an annular projection is provided on the axial surface of said adjusting shaft, the top surface of said annular projection being in contact with the bottom surface of said limiting plate, the bottom surface of said annular projection being for limiting the maximum height of said magnet holder.
9. The local resonance type photonic crystal vibration damping device as claimed in claim 1, wherein the top of the adjustment shaft is fixedly connected to the rotating handle;
furthermore, the top end of the adjusting shaft is fixedly connected with the rotating handle through a locking piece, and the adjusting shaft is matched with the rotating handle through a square insertion block and a square slot.
10. An apparatus, characterized in that a local resonance type phononic crystal vibration damping device according to any one of claims 1 to 9 is provided.
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| CN116384138A (en) * | 2023-04-10 | 2023-07-04 | 山东大学 | Phonon crystal topology optimization method and system containing specific band gap |
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