CN113187847B - A marine magnetorheological elastomer vibration-damping floating raft - Google Patents

Abstract

The invention provides a magnetorheological elastomer vibration reduction floating raft for a ship, which comprises an elastic base, wherein the top end of the elastic base is sequentially provided with a middle raft body and vibration excitation equipment from bottom to top, the elastic base is connected with the middle raft body through a lower-layer vibration isolator, and the middle raft body is connected with the vibration excitation equipment through an upper-layer vibration isolator. The invention can improve the vibration isolation effect of the floating raft system, and can adjust the rigidity of the raft frame according to the change of the excitation load no matter at low frequency or high frequency.

Description

A marine magnetorheological elastomer vibration-damping floating raft

technical field

The invention mainly relates to the technical field of ship vibration reduction, in particular to a marine magnetorheological elastomer vibration reduction floating raft.

Background technique

Floating raft vibration isolation is an effective vibration isolation method, which is used in some machines or ships with high vibration isolation requirements.

According to the small compressor or motor shock-absorbing floating raft device provided by the patent document with the application number of CN201110202032.6, the product includes a primary shock-absorbing device, a secondary shock-absorbing device, a compressor or a motor and a primary shock-absorbing device Connection, the base is connected with the secondary shock absorber. The primary shock absorption device includes an anchoring glue column and a floating raft seat plate, and the compressor or the motor is flexibly connected to the floating raft seat plate through the anchoring glue column. The two-stage shock absorbing device includes a support spring, a buffer rubber pad, an elastic sleeve, a bolt assembly, and the compressor or motor and the base are connected by a two-stage shock absorbing device in a flexible connection and flexible support manner. When the amplitude generated by the compressor or motor is transmitted to the base, it can be reduced by more than 90%, which can greatly improve the working condition of the system and the user's experience.

Although many researchers have improved the structure of the raft, they cannot perform full-frequency intelligent control according to the excitation frequency of the equipment from 0 to 1000 Hz. The raft, as a vibration isolator with many equipment installed, its mechanical properties need to be adjusted according to different The excitation frequency of the equipment is adjusted to achieve the optimal vibration isolation effect.

SUMMARY OF THE INVENTION

The present invention mainly provides a marine magnetorheological elastomer vibration-damping floating raft to solve the technical problems raised in the above-mentioned background art.

The technical scheme adopted by the present invention to solve the above-mentioned technical problems is:

A marine magnetorheological elastomer vibration-damping floating raft, comprising an elastic base, the top of the elastic base is provided with a lower vibration isolator, a middle raft, an upper vibration isolator and vibration excitation equipment arranged in sequence from bottom to top , the upper vibration isolator is provided with multiple;

The intermediate raft is provided with a plurality of magnetorheological elastomers, each magnetorheological elastomer is provided with an excitation coil, the bottom of the magnetorheological elastomer is fixed on the bottom of the intermediate raft, and the top is movable and connected to the bottom of the intermediate raft. The position of one of the upper vibration isolators corresponds to;

The lower vibration isolator includes a plurality of vibration damping springs connected to the lower surface of the intermediate raft and to the upper surface of the elastic base, and a plurality of sets of vibration damping components arranged on the upper surface of the elastic base;

The vibration damping assembly includes first cylinders respectively arranged at both ends of the elastic base, and a scissor-type connecting assembly connecting the execution ends of the piston rods of the two first cylinders. Vibration springs, each of which abuts against the lower surface of the intermediate raft.

Further, the bottom end of the scissor-type connecting assembly is connected with a rotation adjustment mechanism, and the rotation adjustment mechanism includes a groove opened on the top end of the elastic base, and a first electric guide rail fixed in the groove is connected to the groove. The first slider that is slidably connected to the top of the first electric guide rail, the second cylinder that is fixed to the top of the first slider, and the rotating shaft that is fixed to the piston rod of the second cylinder, so that the scissor-type connecting assembly can It is quickly concentrated near the axis of rotation, and the less rigid areas in the intermediate raft are cushioned by the vibration isolation springs on the scissor connection assembly.

Further, a plurality of first balls are embedded in the outer peripheral surface of each of the rotating shafts, and the plurality of first balls are arranged equidistantly one by one around the central axis of the radial plane of the rotating shaft, so as to prevent the space between the rotating shaft and the rotating ring. Generates dry friction, extending the life of the rotating shaft and rotating ring.

Further, the scissors-type connecting assembly is provided with a plurality of rotating rings for the rotating shaft to be inserted through, so as to guide the scissors-type connecting assembly to be quickly concentrated near the rotating shaft, and the vibration isolation springs on the scissors-type connecting assembly are oriented to the middle. The less rigid areas of the raft are cushioned.

Further, the top end of each of the vibration isolation springs is fixed with a support plate abutting against the bottom surface of the intermediate raft body, and the top end of each support plate is embedded with a second ball, thereby preventing the vibration isolation spring. Dry friction is generated with the bottom end surface of the intermediate raft, thereby prolonging the service life of the vibration isolation spring and the intermediate raft.

Further, the magnetic particle content percentage of the magnetorheological elastomer is 27%.

Further, the elastic base includes a vibration damping cover fixed on the bottom end of the lower vibration isolator, a leaf spring fixed on the inner surface of the vibration damping cover, and a bottom end of the leaf spring and connected with the damper. The rubber plate connected with the vibration cover enables the vibration damping cover fixed at the bottom end of the lower vibration isolator and the rubber plate on the ground to further absorb vibration through the leaf spring.

Further, a symmetrically arranged first neodymium magnet is fixed on the inner wall surface of the vibration damping cover, a second neodymium magnet is arranged at the bottom end of the first neodymium magnet, and the second neodymium magnet and the first neodymium magnet are magnetically repelled. , the second neodymium magnet is fixed on the top surface of the rubber plate, and the vibration damping cover is further buffered by the magnetic repulsion between the first neodymium magnet on the vibration damping cover and the second neodymium magnet on the rubber plate .

Further, a sliding mechanism is connected to the top of the first cylinder, and the sliding mechanism includes a second electric guide rail embedded in the bottom end surface of the intermediate raft, slidably connected to the second electric guide rail and fixed to the first electric guide rail. A second sliding block on the top surface of the cylinder makes it convenient for the first cylinder to quickly control the scissor-type connecting assembly to fold and stretch, preventing the first cylinder from protruding out of the vibration-damping raft due to being too long, thereby affecting the use.

Further, a PLC controller is fixed on the outside of the intermediate raft, and the PLC controller is electrically connected with the first cylinder, the second cylinder and the excitation coil to realize data interaction, so that the dynamic effect of the resonance load of different frequencies can be solved. response, which provides the basis for the subsequent evaluation of vibration damping performance.

Compared with the prior art, the beneficial effects of the present invention are:

First, the magnetorheological elastomer floating raft can improve the vibration isolation effect of the floating raft system, and the stiffness of the raft can be adjusted according to the change of the excitation load no matter at low frequency or high frequency. For a raft that needs to be installed with multiple devices, it is necessary to adjust the vibration isolation effect of the raft according to the vibration frequencies of different devices. In the vibration range of 0~1000Hz, the vibration isolation effect is excellent, up to 45dB.

Second, the present invention can realize vibration isolation of low frequency and high frequency at the same time, specifically: taking the excitation frequency as the guide, it is proposed to adjust the local stiffness of the raft by changing the current of the built-in excitation coil, and implement the optimal vibration isolation by equipment. Compared with the traditional raft, the variable stiffness characteristic of the magnetorheological elastomer raft provides a new idea for the design of the floating raft vibration reduction system.

The present invention will be explained in detail below with reference to the accompanying drawings and specific embodiments.

Description of drawings

Fig. 1 is the overall structure schematic diagram of the present invention;

Fig. 2 is the axonometric view of the present invention;

Fig. 3 is the exploded view of the present invention;

4 is a schematic structural diagram of a vibration damping assembly of the present invention;

5 is a schematic structural diagram of an elastic base of the present invention;

6 is a schematic structural diagram of a scissors-type connecting assembly of the present invention;

Fig. 7 is the structural representation of the rotation adjustment mechanism of the present invention;

Fig. 8 is an enlarged view of the structure of the A region in Fig. 4;

Figure 9 is a graph of stiffness versus current;

Figure 10 is a comparison curve of the power flow drop of 1~5A;

Figure 11 is a comparison curve of the power flow drop of 6~10A;

FIG. 12 is a graph showing the power flow drop and excitation current of optimal control.

In the figure: 10, elastic base; 11, vibration damping cover; 12, leaf spring; 13, rubber plate; 20, lower vibration isolator; 21, vibration damping assembly; 211, first cylinder; 2121, rotating ring; 213, vibration isolation spring; 2131, second ball; 2132, support plate; 214, rotating adjustment mechanism; 2141, rotating shaft; 2142, second cylinder; 2143, first electric guide rail; 2144, concave Slot; 2145, first slider; 2146, first ball; 215, sliding mechanism; 2151, second electric guide rail; 2152, second slider; 22, damping spring; 30, middle raft; 31, excitation coil ; 32, magnetorheological elastomer; 33, PLC controller; 40, upper vibration isolator; 50, excitation equipment.

Detailed ways

In order to facilitate the understanding of the present invention, the present invention will be described more fully hereinafter with reference to the related drawings, in which several embodiments of the present invention are given, but the present invention can be implemented in different forms and is not limited to the description in the text rather, these embodiments are provided so that this disclosure will be thorough and complete.

It should be noted that when an element is referred to as being "fixed" to another element, it may be directly on the other element or intervening elements may be present, and when an element is referred to as being "connected" to another element, it may be The terms "vertical," "horizontal," "left," "right," and similar expressions used herein are for the purpose of illustration only.

Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly associated by one of ordinary skill in the technical field of the present invention, and the terminology used herein in the description of the present invention is used for the purpose of describing specific embodiments. For the purpose of, and not intended to limit, the present invention, as used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.

Embodiments, please refer to Figures 1-8. In a preferred embodiment of the present invention, a marine magnetorheological elastomer vibration-damping floating raft includes an elastic base 10, and the top of the elastic base 10 is provided with a floating raft. The lower vibration isolator 20, the middle raft 30, the upper vibration isolator 40 and the vibration excitation device 50 are arranged in sequence from bottom to top, and there are multiple upper vibration isolators 40;

The intermediate raft body 30 is provided with a plurality of magnetorheological elastic bodies 32 , each magnetorheological elastic body 32 is provided with an excitation coil 31 , and the bottom of the magnetorheological elastic body 32 is fixed to the bottom of the intermediate raft body 30 , the top is movable and corresponds to the position of one of the upper vibration isolators 40;

The lower vibration isolator 20 includes a plurality of damping springs 22 connected to the lower surface of the intermediate raft 30 and to the upper surface of the elastic base 10, and a plurality of sets of vibration damping components 21 disposed on the upper surface of the elastic base 10;

The vibration damping assembly 21 includes first air cylinders 211 respectively disposed at both ends of the elastic base 10 , and a scissor-type connecting assembly 212 connecting the execution ends of the piston rods of the two first air cylinders 211 . The bends are provided with vibration isolation springs 213, and each vibration isolation spring 213 abuts against the lower surface of the intermediate raft 30;

It should be noted that, in this embodiment, based on the vibration power flow formula of the vibration system: P = F • V , F and V are the instantaneous values representing the force and speed at a certain point of the system, so that the excitation coil 31 is connected to the When the current flows in the same direction, the bottom of the excitation coil 31 is set as a fixed constraint, inside the intermediate raft 30, the Maxwell stress boundary condition is set at the boundary, and a z-direction resonance load of 0~1000Hz and a size of 2000N is applied to the top surface of the equipment model. The model is meshed with free tetrahedrons. When solving, the research steps for Comsol are set as follows. Step 1 obtains the magnetic field generated by the four excitation coils 31, and step 2 realizes the force-magnetic coupling to obtain the stress distribution under the magnetic field. Steps 3 and 4 are to solve the response of the coupled intermediate raft 30 under the resonant load of 0 to 1000 Hz. According to the solution results, the power flow data is extracted from the top of the upper vibration isolator 40 and the bottom of the lower vibration isolator 20. As the input power flow and the output power flow respectively, the power flow drop is calculated in Matlab, and the excitation current of the excitation coil 31 can be adjusted to improve the vibration reduction effect of the floating raft under different excitation loads. In order to quantitatively control the vibration reduction of the floating raft, it can be extracted The optimal excitation current corresponding to each frequency band, that is, the current corresponding to the maximum power flow drop value, so far, for different excitation devices 50 installed on the same raft, the above current values can be passed according to the excitation load frequency, Set its corresponding power flow drop;

越接近

时，则越小，说明隔振效果越差；根据前面的研究，电流越大，磁流变弹性体的浮筏整体刚度越大，因此对于300~600Hz中等频率激振载荷，励磁电流为6~10A时的隔振效果较好，能达到30dB左右。对于600Hz以上的高频载荷，电流为3、4A时效果较好,也能达到30dB左右。这恰好符合低频高刚、高频低刚的减振设计理念；从图中还可以看出，对于低刚的筏体（通入1~5A电流），在高频阶段相较于高刚筏体（通入6~10A电流）易出现共振峰，而高刚筏体则表现得比较“平整”，这是因为高刚筏体抵抗变形的能力较强，振动过程中吸收的能量更多。Further, in order to compare the vibration isolation effect, the ordinary plate raft and the hollow raft were calculated respectively, and according to the difference calculation results, the power flow data were extracted from the top of the upper vibration isolator 40 and the bottom of the lower vibration isolator 20. , as the input power flow and the output power flow, respectively, and calculate the power flow drop in Matlab. The results are shown in Figures 10 and 11. It can be seen from the figure that in the low frequency range below 300Hz, the number of troughs appears more , this is because the natural frequency is mainly concentrated in the low frequency band; when the system resonates, the value of the input power flow is not much different from the value of the output power flow, namely

the closer

When , the smaller it is, the worse the vibration isolation effect is; according to the previous research, the greater the current, the greater the overall stiffness of the floating raft of the magnetorheological elastomer. Therefore, for the medium frequency excitation load of 300~600Hz, the excitation current is 6 The vibration isolation effect is better at ~10A, which can reach about 30dB. For high-frequency loads above 600Hz, the effect is better when the current is 3 or 4A, and it can also reach about 30dB. This is exactly in line with the vibration reduction design concept of low-frequency high-rigidity and high-frequency low-rigidity; it can also be seen from the figure that for a low-rigidity raft (with a current of 1~5A), in the high-frequency stage, compared with a high-rigidity raft The high-rigidity raft is more “flat” because the high-rigidity raft is more resistant to deformation and absorbs more energy during vibration.

Further, the four installation points of the upper vibration isolator 40 are installed directly above the excitation coil 31, because the magnetic field generated in this area is locally strongest and has the best magneto-induced effect, so that the local stiffness can be adjusted. In other areas of the raft, a strong magnetic field can also be generated through the superposition of the magnetic fields of the excitation coils 31, so that the overall stiffness of the raft can be adjusted;

Further, guided by the excitation frequency, it is proposed that the local stiffness of the intermediate raft 30 is adjusted by changing the current of the built-in excitation coil 31, and the optimal vibration isolation of the excitation device 50 is implemented by equipment;

Further, the four excitation coils 31 evenly arranged on the middle raft 30, the excitation coil 31 has a radius of 100mm and a height of 210mm. The stiffness is determined by the magnitude of the reaction force on the bottom surface. A current of 0~10A is passed into the excitation coil 31 in turn. The calculated stiffness value is shown in Figure 9. It can be seen from the figure that with the increase of the current, the stiffness presents The nonlinearity increases, because the elastic modulus of the magnetorheological elastomer 32 changes nonlinearly with the external magnetic field;

Further, adjusting the current generated by the excitation coil 31 can improve the vibration reduction effect of the floating raft under different excitation loads. In order to quantitatively control the vibration reduction of the floating raft, the optimal excitation current corresponding to each frequency band, that is, the maximum power can be extracted. The current corresponding to the flow drop value, so far, for different equipment installed on the same raft, the above current value can be passed in according to its excitation load frequency, and the corresponding power flow drop is shown in Figure 12.

Specifically, please refer to FIGS. 3, 4 and 7. In another preferred embodiment of the present invention, the bottom end of the scissors-type connecting assembly 212 is connected with a rotation adjusting mechanism 214, and the rotating adjusting mechanism 214 includes a The groove 2144 at the top of the elastic base 10 is fixed to the first electric guide rail 2143 inside the groove 2144, and the first slider 2145 slidably connected to the top of the first electric guide rail 2143 is fixed to the first electric guide rail 2143. A second cylinder 2142 at the top of a slider 2145, and a rotating shaft 2141 fixed on the piston rod of the second cylinder 2142, the outer peripheral surface of each rotating shaft 2141 is embedded with a plurality of first balls 2146, a plurality of The first balls 2146 are arranged equidistantly one by one around the central axis of the radial plane of the rotating shaft 2141. The scissor-type connecting assembly 212 is provided with a plurality of rotating rings 2121 for the rotating shaft 2141 to pass through. The tops of the vibration springs 213 are all fixed with support discs 2132 abutting against the bottom surface of the intermediate raft 30 , and the tops of each of the support discs 2132 are embedded with second balls 2131 ;

It should be noted that, in this embodiment, when the first electric guide rail 2143 on the elastic base 10 drives the first sliding block 2145 thereon to slide, the second air cylinder 2142 is fixed on the first sliding block 2145, thereby Drive the second cylinder 2142 and the rotating shaft 2141 on its piston rod to translate until the rotating shaft 2141 moves to the area with poor rigidity in the middle raft 30 under the control of the PLC controller 33, and then passes through the second cylinder 2142 piston rod Drive the rotating shaft 2141 to rise until the rotating shaft 2141 passes through the hinge point of the connecting rod in the scissor-type connecting assembly 212, so that the scissors-type connecting assembly 212 can rotate with the rotating shaft 2141 as the rotation center. At this time, the scissors-type connecting assembly 212 It can be quickly concentrated near the rotating shaft 2141, and the area with poor rigidity in the intermediate raft body 30 can be buffered by the vibration isolation spring 213 on the scissor-type connecting assembly 212;

Further, the rotating shaft 2141 is made to roll on the rotating ring 2121 on the scissors-type connecting assembly 212 by the first ball 2146 on it, so as to prevent dry friction between the rotating shaft 2141 and the rotating ring 2121, thereby extending the length of the rotating shaft 2141 and the rotating ring 2121. The service life of the rotating ring 2121;

Further, since the scissor-type connecting assembly 212 is composed of a plurality of mutually hinged links, the scissors-type connecting assembly 212 guides the rotating shaft 2141 to pass through the rotating ring 2121 provided at the hinge of the two links, so that the connecting rods are connected in this way. The rotating ring 2121 rotates as the center of rotation, so as to guide the scissor-type connecting assembly 212 to quickly converge to the vicinity of the rotating shaft 2141, and buffer the area with poor rigidity in the intermediate raft 30 through the vibration isolation spring 213 on the scissor-type connecting assembly 212 ;

Further, when the vibration isolation spring 213 is translated under the driving of the scissor-type connecting assembly 212, the second ball 2131 on the support plate 2132 of the vibration isolation spring 213 rolls on the bottom surface of the raft body 30, thereby preventing the isolation Dry friction is generated between the vibration spring 213 and the bottom end surface of the intermediate raft body 30 , thereby prolonging the service life of the vibration isolation spring 213 and the intermediate raft body 30 .

Specifically, please refer to FIGS. 2 , 3 and 4 emphatically. In another preferred embodiment of the present invention, the percentage of the magnetic particle content of the magnetorheological elastomer 32 is 27%;

It should be noted that, in this embodiment, the optimal particle content percentage of the magnetorheological elastomer is 27%. Based on this study, the parameters of the isotropic magnetorheological elastomer with a particle volume fraction of 30% are used. The parameters are shown in Table 1;

Table 1 Parameters of magnetorheological elastomer raft

Specifically, please refer to FIGS. 1 , 2 and 5 emphatically. In another preferred embodiment of the present invention, the elastic base 10 includes a vibration damping cover 11 fixed on the bottom end of the lower vibration isolator 20 . The plate spring 12 on the inner surface of the damping cover 11, and the rubber plate 13 fixed on the bottom end of the plate spring 12 and inserted into the damping cover 11, the inner wall surface of the damping cover 11 is fixed with a rubber plate 13. Symmetrically arranged first neodymium magnets 111, the bottom end of the first neodymium magnet 111 is provided with a second neodymium magnet 131, the second neodymium magnet 131 and the first neodymium magnet 111 magnetically repel, the second neodymium magnet 131 Fixed on the top surface of the rubber plate 13, the top of the first cylinder 211 is connected with a sliding mechanism 215, the sliding mechanism 215 includes a second electric guide rail 2151 embedded in the bottom surface of the intermediate raft 30, and is connected with the The second electric guide rail 2151 is slidably connected and fixed to the second slider 2152 on the top surface of the first cylinder 211;

It should be noted that, in this embodiment, the vibration can be further absorbed by the leaf spring 12 between the vibration damping cover 11 fixed at the bottom end of the lower vibration isolator 20 and the rubber plate 13 on the ground;

Further, when the vibration damping cover 11 is moved downward, the first neodymium magnet 111 on the vibration damping cover 11 and the second neodymium magnet 131 on the rubber plate 13 are magnetically repelled, thereby further buffering the vibration damping cover 11 ;

Further, the first air cylinder 211 and the second sliding block 2152 thereon can be slid below the area with poor rigidity in the middle raft 30 by means of the second electric guide rail 2151 , thereby facilitating the first air cylinder 211 to quickly control the scissor-type connecting assembly 212 It is folded and stretched to prevent the first cylinder 211 from extending out of the vibration damping raft due to being too long, thereby affecting the use.

Specifically, please refer to the accompanying drawings 1, 2, 3 and 4. In another preferred embodiment of the present invention, a PLC controller 33 is fixed outside the intermediate raft 30, and the PLC controller 33 is connected to the first The cylinder 211, the second cylinder 2142 and the excitation coil 31 are electrically connected to realize data exchange;

It should be noted that, in this embodiment, because the PLC controller 33 is electrically connected to the first cylinder 211, the second cylinder 2142 and the excitation coil 31, and because the system is a complex coupling between force fields, magnetic fields and vibrations During the process, the PLC controller 33 uses the finite element method to input the parameters such as mass, stiffness and damping of each part into Comsol, and then solves it. Comsol can calculate the natural frequency of the system under the condition of force-magnetic coupling and carry out modal analysis. According to the research, the dynamic response can be solved for the resonance load of different frequencies, which provides a basis for the subsequent evaluation of the vibration reduction performance.

The specific operation mode of the present invention is as follows:

When using the vibration-damping floating raft, based on the vibration power flow formula of the vibration system: P = F • V , F and V are the instantaneous values of the acting force and velocity at a certain point of the system, respectively, so that the excitation coil 31 is connected to the same direction. When the current is flowing, the bottom of the excitation coil 31 is set as a fixed constraint, inside the intermediate raft 30, the Maxwell stress boundary condition is set at the boundary, and a z-direction resonance load of 0~1000Hz and a size of 2000N is applied to the top surface of the equipment model;

Since the PLC controller 33 is electrically connected to the first cylinder 211, the second cylinder 2142 and the excitation coil 31, and because the system is a complex coupling process between force field, magnetic field and vibration, the PLC controller 33 adopts the finite element method. , input the parameters such as mass, stiffness and damping of each part into Comsol, and then solve it. Comsol can calculate the natural frequency of the system under the condition of force-magnetic coupling and conduct modal research, and can solve the effect of resonance loads of different frequencies. Dynamic response, which provides a basis for subsequent evaluation of vibration reduction performance;

The model is meshed with free tetrahedrons. When solving, the research steps for Comsol are set as follows. Step 1 obtains the magnetic field generated by the four excitation coils 31, and step 2 realizes the force-magnetic coupling to obtain the stress distribution under the magnetic field. Steps 3 and 4 are to solve the response of the coupled intermediate raft 30 under the resonant load of 0 to 1000 Hz. According to the solution results, the power flow data is extracted from the top of the upper vibration isolator 40 and the bottom of the lower vibration isolator 20. As the input power flow and the output power flow respectively, the power flow drop is calculated in Matlab, and the excitation current of the excitation coil 31 can be adjusted to improve the vibration reduction effect of the floating raft under different excitation loads. In order to quantitatively control the vibration reduction of the floating raft, it can be extracted The optimal excitation current corresponding to each frequency band, that is, the current corresponding to the maximum power flow drop value, so far, for different excitation devices 50 installed on the same raft, the above current value can be passed according to the excitation load frequency. Set its corresponding power flow drop.

The present invention has been exemplarily described above in conjunction with the accompanying drawings. Obviously, the specific implementation of the present invention is not limited by the above-mentioned manner, as long as the non-substantial improvement of the method concept and technical solution of the present invention is adopted, or the present invention is modified without improvement. If the concept and technical solutions of the invention are directly applied to other occasions, they all fall within the protection scope of the present invention.

Claims (9)

1. The marine magneto-rheological elastomer vibration reduction buoyant raft comprises an elastic base (10), and is characterized in that the top end of the elastic base (10) is sequentially provided with a middle raft body (30) and vibration excitation equipment (50) from bottom to top, the elastic base (10) is connected with the middle raft body (30) through a lower-layer vibration isolator (20), and the middle raft body (30) is connected with the vibration excitation equipment (50) through an upper-layer vibration isolator (40);

the middle raft body (30) is internally provided with a plurality of magneto-rheological elastomers (32), an excitation coil (31) is arranged in each magneto-rheological elastomer (32), the bottom of each magneto-rheological elastomer (32) is fixed at the bottom of the middle raft body (30), and the top of each magneto-rheological elastomer is movable and corresponds to one upper-layer vibration isolator (40);

the lower-layer vibration isolator (20) comprises a plurality of damping springs (22) which are connected with the lower surface of the middle raft body (30) and the upper surface of the elastic base (10), and a plurality of groups of damping assemblies (21) which are arranged on the upper surface of the elastic base (10);

the damping assembly (21) comprises first air cylinders (211) respectively arranged at two ends of the elastic base (10) and a scissors type connecting assembly (212) for connecting the actuating ends of piston rods of the two first air cylinders (211), each bending part of the scissors type connecting assembly (212) is provided with a vibration isolation spring (213), and each vibration isolation spring (213) abuts against the lower surface of the middle raft body (30);

scissors formula coupling assembling (212) bottom is connected with rotation adjustment mechanism (214), rotation adjustment mechanism (214) are including seting up in recess (2144) on elastic base (10) top is fixed in inside first electronic guide rail (2143) on recess (2144), with first electronic guide rail (2143) top sliding connection's first slider (2145), be fixed in second cylinder (2142) on first slider (2145) top, and be fixed in rotation axis (2141) on the piston rod of second cylinder (2142).

2. The magnetorheological elastomer vibration damping raft for ships according to claim 1, wherein a plurality of first balls (2146) are embedded in the outer circumferential surface of each rotating shaft (2141), and the first balls (2146) are arranged around the central axis of the radial plane of the rotating shaft (2141) one by one at equal intervals.

3. The marine magnetorheological elastomer vibration damping raft according to claim 2, wherein the scissor-type connection assembly (212) is provided with a plurality of rotating rings (2121) for the rotating shaft (2141) to penetrate through.

4. The marine magnetorheological elastomer vibration damping raft according to claim 1, wherein a support plate (2132) abutting against the bottom end surface of the intermediate raft body (30) is fixed at the top end of each vibration isolation spring (213), and second balls (2131) are embedded in the top end of each support plate (2132).

5. The marine magnetorheological elastomer vibration damped raft of claim 1, wherein the magnetorheological elastomer (32) has a magnetic particle content percentage of 27%.

6. The marine magnetorheological elastomer vibration damping raft according to claim 1, wherein the elastic base (10) comprises a vibration damping cover (11) fixed to the bottom end of the lower vibration isolator (20), a plate spring (12) fixed to the inner surface of the vibration damping cover (11), and a rubber plate (13) fixed to the bottom end of the plate spring (12) and inserted into the vibration damping cover (11).

7. A magnetorheological elastomer vibration damping raft according to claim 6, wherein the inner wall surface of the vibration damping cover (11) is fixed with symmetrically arranged first neodymium magnets (111), the bottom end of the first neodymium magnet (111) is provided with a second neodymium magnet (131), the second neodymium magnet (131) is magnetically repulsive to the first neodymium magnet (111), and the second neodymium magnet (131) is fixed on the top end surface of the rubber plate (13).

8. The marine magnetorheological elastomer vibration-damping raft according to claim 1, wherein a sliding mechanism (215) is connected to the top end of the first cylinder (211), the sliding mechanism (215) comprises a second electric rail (2151) embedded in the bottom end surface of the intermediate raft (30), and a second slider (2152) slidably connected to the second electric rail (2151) and fixed to the top end surface of the first cylinder (211).

9. The marine magnetorheological elastomer vibration-damping raft according to claim 1, wherein a PLC (33) is fixed outside the intermediate raft body (30), and the PLC (33) is electrically connected with the first cylinder (211), the second cylinder (2142) and the excitation coil (31) to realize data interaction.

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