CN206778581U - A kind of multimachine drives motor synchronizing self-balancing type vibrator - Google Patents
A kind of multimachine drives motor synchronizing self-balancing type vibrator Download PDFInfo
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Abstract
The utility model belongs to grinding device, and a kind of multimachine drives motor synchronizing self-balancing type vibrator, the characteristics of combining ball mill and vibrating mill.Using the structure that body centre and power spindle are eccentric,Using cylinder itself as vibrator,Realize dither,Grinding energy is big,Possess multiple cylinders simultaneously,Operating efficiency is high,Reach stable self-balancing run-in synchronism,Itself circular motion is realized in each eccentric cylinder revolution,Multiple eccentric cylinders realize that motor synchronizing operates,When multiple the same eccentric cylinder circumference uniform distributions are in the barycenter periphery of vibrational system,Because their phase difference is stable at Pi/n (n represents the number of eccentric cylinder) place,Exciting force caused by each eccentric cylinder is caused to be cancelled out each other,Cause vibration body depressed dynamic,Vibration body is reached with this 0 is actuated to basis,It can realize that each eccentric cylinder realizes high speed circular motion,And can ensures that the vector of the vibrational excitation to basis makes a concerted effort to be zero,So as to meet the vibration noise environmental requirement of national regulation.
Description
Technical Field
The utility model belongs to a grinding device, a multimachine drive self-synchronizing self-balancing vibration ball mill.
Background
Ball mill: the operations of vibration ball milling, fine crushing and the like are widely applied to the industries of mineral separation, construction, chemistry, pharmacy and the like. In the mineral processing industry, when the useful minerals are distributed in the ore in fine particles, the ore must be ground to 0.3 to 0.1 mm, and sometimes 0.05 to 0.07 mm or less, in order to separate the gangue from the ore and to separate the various useful minerals from each other. The grinding fineness and the mineral separation index have a close relationship, and the metal recovery rate is increased along with the reduction of the grinding fineness to a certain extent. Thus, the recovery rate and yield of metal can be improved by properly reducing the grinding fineness of the ore. The power consumed by ore grinding accounts for more than 30% of the total power consumption of the concentrating mill. Therefore, the ore grinding operation occupies an important position in the process flow of ore dressing.
The grinding is carried out in a ball mill. The cylindrical mill has a hollow cylinder 1 with hollow journals 4 and 5 at each end with end caps 2 and 3, the journals being supported on bearings. The cylinder is filled with crushing media (steel balls, steel bars, gravels and the like) with various diameters. When the cylinder rotates around the horizontal axis at a specified rotating speed, the crushing medium and ore in the cylinder rise to a certain height along with the cylinder wall under the action of centrifugal force and friction force, and then fall or roll off freely after separating from the cylinder wall. The grinding of the ore is mainly based on the impact force when the crushing medium falls and the grinding action when the crushing medium moves. The ore is continuously fed from the hollow journal of one section of the cylinder, the ground product is continuously discharged through the hollow journal of the other end of the cylinder, and the movement of the ore in the cylinder is realized by the pressure of the continuously fed ore. During wet grinding, the ore is carried away by water flow, and during dry grinding, the ore is carried away by air flow pumped out of the cylinder.
The common ball mill has high weight, low crushing energy, large granularity of finished products, large occupied area and complex structure.
SUMMERY OF THE UTILITY MODEL
The utility model overcomes the problem that prior art exists provides a multimachine drive self-synchronizing self-balancing formula vibration ball mill under the off-resonance condition, adopts barrel center and the eccentric structure of power main shaft, regards barrel self as the vibration exciter, realizes high-frequency vibration, and the grinding energy is big, possess a plurality of barrels simultaneously, and work efficiency is high, reaches stable self-balancing run-in-step. When the synchronous stable operation, the self circular motion of each eccentric cylinder is realized, and simultaneously the self synchronous operation of a plurality of eccentric cylinders is realized, so when a plurality of identical eccentric cylinders are circumferentially and uniformly distributed at the periphery of the mass center of the vibration system, the phase difference of the eccentric cylinders is stabilized at Pi/n (n represents the number of the eccentric cylinders), so that the excitation force generated by each eccentric cylinder is mutually counteracted, and the vibration machine body does not vibrate, thereby achieving the purposes that the excitation of the vibration machine body to the foundation is 0, the noise is low, and the national environmental protection requirement is met. In a word, the utility model discloses a mechanism and principle can realize that every eccentric barrel realizes high-speed circular motion, can guarantee again that the resultant force of vector to the vibration excitation of basis is zero to satisfy the vibration noise environmental protection requirement of national regulation.
The technical scheme of the utility model is that:
a multi-machine driven self-synchronizing self-balancing type vibrating ball mill comprises a charging barrel, a flange A, a flange B, a rotating shaft A, a rotating shaft B, an upper box body, a middle box body, a bearing with a seat, a vibration isolation spring, a lower box body, a hydraulic cylinder, an end cover, a barrel body, a flexible coupling, a motor, a main shaft, a lining plate, a helical blade, a screen and a base; the upper box body, the middle box body and the lower box body are fixedly connected, the base is fixed on the ground, the lower box body is supported on a hydraulic cylinder on the upper portion of the base through a vibration isolation spring, a bearing with a seat is fixed in the box body, more than three cylinder bodies are respectively matched and connected with the bearing with the seat through a rotating shaft, the circumferences of the cylinder bodies are uniformly distributed in a vibration-participating mass center, the eccentric distance of an eccentric shaft in each cylinder body is 4-20 mm, and the eccentric shaft is fixedly connected with the cylinder body; the end cover is fixedly connected with one end of the barrel, the inner wall of the barrel is provided with a lining plate, the side of the end cover of the barrel is sequentially provided with a helical blade and a screen mesh which are fixedly connected with the barrel, and the outer wall of the barrel is provided with a feeding port; the motor is connected with the main shaft of the cylinder through a flexible coupling; the flexible coupling and the bearing with the seat are connected through the matching of the shaft and the bearing.
The utility model has the advantages that 1) a plurality of cylinders work synchronously, and the output is high; 2) the vibration machine works under high-frequency excitation, and the amplitude is large; 3) the motor rotates forwards to crush and grind, the hydraulic cylinder jacks up when rotating backwards, the cylinder body is inclined to discharge, the operation is simple, and the automatic production is convenient to realize; 4) the specified motor rotation direction is used, self-synchronization self-balancing is realized, the excitation to the matrix is 0, and the environment-friendly requirement of vibration noise specified by the state is met.
Drawings
FIG. 1 is a schematic diagram of a conventional ball mill;
FIG. 2 is a block diagram;
FIG. 3 is a top view of FIG. 3;
FIG. 4 is a left side view of FIG. 3;
FIG. 5 is an n-machine dynamics model;
FIG. 6 is a schematic diagram of a 4-machine scheme 1;
FIG. 7 is a schematic diagram of a 4-machine scheme 2;
FIG. 8 is a schematic diagram of a 4-machine scheme 3;
FIG. 9 is a schematic diagram of a 3-machine;
FIG. 10 is a schematic diagram of a k-machine;
in the figure: 1, a charging barrel; 2, a flange A; 3, flange B; 4, rotating a shaft A; 5, rotating a shaft B; 6, putting the box body on the box body; 7, a middle box body; 8 bearing with base; 9 vibration isolation springs; 10, a lower box body; 11 hydraulic cylinders; 12 end caps; 13 a cylinder body; 14, a screw; 15 a flexible coupling; 16 motor; 17 a main shaft; 18 liner plates; 19 a feeding port; 20 helical blades; 21 a screen mesh; 22, a base.
Detailed Description
A multi-machine driven self-synchronizing self-balancing type vibrating ball mill comprises a charging barrel 1, a flange A2, a flange B3, a rotating shaft A4, a rotating shaft B5, an upper box 6, a middle box 7, a seated bearing 8, a vibration isolation spring 9, a lower box 10, a hydraulic cylinder 11, an end cover 12, a barrel 13, a flexible coupling 15, a motor 16, a main shaft 17, a lining plate 18, a helical blade 20, a screen 21 and a base 22; the vibration isolation device comprises an upper box body, a middle box body and a lower box body, wherein the upper box body, the middle box body and the lower box body are fixedly connected, the base is fixed on the ground, the lower box body is supported on a hydraulic cylinder on the upper part of the base through a vibration isolation spring, a bearing with a seat is fixed in the box body, more than three cylinder bodies are respectively matched and connected with the bearing with the seat through a rotating shaft, the circumferences of the cylinder bodies are uniformly distributed in a vibration isolation mass center, the diameter of each cylinder body is 200mm (adjustable according to actual engineering requirements), the eccentric distance of an; the end cover is fixedly connected with one end of the barrel, the inner wall of the barrel is provided with a lining plate, the side of the end cover of the barrel is sequentially provided with a helical blade and a screen mesh which are fixedly connected with the barrel, and the outer wall of the barrel is provided with a feeding port 19; the motor is connected with the main shaft of the cylinder through a flexible coupling; the flexible coupling and the bearing with the seat are connected through the matching of the shaft and the bearing.
This utility model is to all can realize more than 3 machines to the n machine is the illustration principle:
step 1: establishing a dynamic model and a motion differential equation:
the dynamic model of the system considered is shown in fig. 2, with n eccentric rotors mounted on a rigid frame and driven by n induction motors, respectively, with q rotating clockwise and p rotating counterclockwise. The motion of the rigid frame is assumed to be planar motion, the frame is fixed to the frame, and the origin is the balance point of the center of mass of the rigid frame. The plane motion coordinate is represented by x, y, and wobbles around its centroid by ψ (ψ)<<1) And (4) showing. Each eccentric rotor rotates around its own rotation axis toi-1, 2, …, p, p +1, …, p + q, βiThe included angle between the connecting line of the eccentric rotor center and the system centroid o point and the x axis is shown, the x axis in a coordinate system xoy is in the horizontal direction, the x 'axis follows the translation of the system in a coordinate system x' o 'y', the included angle between the x axis and the x axis is psi, and when the device is static, the psi is 0 degree.
Order to(h is p + q) is a generalized coordinate, and a system motion differential equation is obtained by using a Lagrange equation
Wherein,
m is the rigid frame mass; j. the design is a squaremIs moment of inertia of rigid frame, miIs the mass of the eccentric rotor i, /)0Is the center of rotation o of the eccentric rotor iiThe distance between the frame and the center of mass of the rigid frame; k is a radical ofx,kyAnd kψIs the stiffness of the system in the corresponding direction, fxfy,fψIs the damping coefficient in the x, y, psi direction, fiIs the damping coefficient of the rotor i of the motor, leIs the equivalent radius of gyration, T, of the vibration system about the center of mass of the rigid frameeiIs the electromagnetic torque of the electric machine i, J0iIs the moment of inertia of the eccentric rotor i. Assuming that the eccentric radii of the plurality of eccentric rotors are the same, i.e. r1＝r2＝…＝rhR. The rotational inertia of the motor rotor is small and negligible.Andrespectively represent d ·/dt and d2·/dt2。
Step 2: synchronization and stability conditions for deriving system to realize synchronization
Average angular velocity of a plurality of eccentric rotors due to periodic vibration of a vibration systemThe period of time of (a) varies. If the minimum common of a plurality of eccentric rotor periodsMultiple of T0Then through T0The average value of the average angular velocities of the plurality of eccentric rotors must be a constant value over time, i.e. a constant value
We set the following:
here, ,andrespectively (attention to)Andthe function being that time t) is with respect to ωm0Andinstantaneous coefficient of variation.
Based on the formula (3), there are
Here, Fi(α1,α2,…,αh-1) Is α1,α2,…,αh-1Is a linear function ofIs thatIs a linear function of (a).iThe dimensionless angular velocity disturbance parameter of the eccentric rotor i is expressed in equation (4), i.e.
We define m1As a standard rotor m0That is, m1＝m0And m isi＝ηim0(0<ηi≤1,i＝1,2，…,h,η11) in the first three formulas of formula (1) at steady state, on the premise that the small damped vibration system is not resonantAnd can be ignored. The system responds in the x-y-and psi-directions
Here, ,
angular velocity of induction motor at omegam0Electromagnetic torque meter with stable operationShown asHere Te0iAndrespectively, angular velocity of omegam0The effective electromagnetic output torque and the angular velocity stiffness coefficient of the induction machine. After dimensionless processing, we obtain the frequency capture equation for realizing synchronization of the system as follows:
here, the
The synchronization condition for realizing the synchronization of the system is as follows:
the stability conditions of the angular velocity of the system are:
ai′j>0,det(A2′)>0,det(A3′)>0,…,det(A′)>0, (8)
here, a ═ ai′j)h×hAnd B ═ Bi′j)h×hRepresenting the rows and columns of the matrix A and BIn the formula (II), the compound (II) is shown in the specification,
in addition, in order to ensure the stability of the system, in addition to the speed stability, the phase difference stability of a plurality of eccentric rotors of the system is also considered.
In formula (6), inAnd (c) linearizing u equal to 0, and taking into accountTo obtain
This (·)0To representAndthe value of (c).
Rearrangement of formula (9) to give
In the formula Δ α ═ vexp (λ t), the determinant equation det (D- λ I) ═ 0 is obtained, and using the Routh-Hurwitz criterion, the solution of the phase difference is stable if the eigenvalues λ of the generalized system all have negative real parts. The stability of the whole vibration system can be ensured only if the speeds of a plurality of eccentric rotors and the phase difference of the eccentric rotors are stable.
According to the number of the cylinders, the method can be divided into two cases:
when four cylinders are used, the four cylinders are uniformly distributed around the center of mass of the vibration body, and three operation schemes are provided; when the number of the cylinders is 3 or more than 5, the cylinder circumferences are evenly distributed on the periphery of the center of the body participating in vibration, and only one operation scheme is provided. It must be emphasized that: in any case, the vibration bodies are required to be evenly distributed on the periphery of the mass center of the vibration bodies.
Claims (1)
1. A multi-machine driven self-synchronizing self-balancing type vibrating ball mill is characterized by comprising a charging barrel, a flange A, a flange B, a rotating shaft A, a rotating shaft B, an upper box body, a middle box body, a bearing with a seat, a vibration isolation spring, a lower box body, a hydraulic cylinder, an end cover, a barrel body, a flexible coupling, a motor, a main shaft, a lining plate, a helical blade, a screen and a base; the upper box body, the middle box body and the lower box body are fixedly connected, the base is fixed on the ground, the lower box body is supported on a hydraulic cylinder on the upper portion of the base through a vibration isolation spring, a bearing with a seat is fixed in the box body, more than three cylinder bodies are respectively matched and connected with the bearing with the seat through a rotating shaft, the circumferences of the cylinder bodies are uniformly distributed in a vibration-participating mass center, the eccentric distance of an eccentric shaft in each cylinder body is 4-20 mm, and the eccentric shaft is fixedly connected with the cylinder body; the end cover is fixedly connected with one end of the barrel, the inner wall of the barrel is provided with a lining plate, the side of the end cover of the barrel is sequentially provided with a helical blade and a screen mesh which are fixedly connected with the barrel, and the outer wall of the barrel is provided with a feeding port; the motor is connected with the main shaft of the cylinder through a flexible coupling; the flexible coupling and the bearing with the seat are connected through the matching of the shaft and the bearing.
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109647597A (en) * | 2018-12-17 | 2019-04-19 | 东北大学 | A kind of multimachine driving circular motion vibro-crusher |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109647597A (en) * | 2018-12-17 | 2019-04-19 | 东北大学 | A kind of multimachine driving circular motion vibro-crusher |
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