RU2710314C1 - Method for changing and adjusting the dynamic state of a vibration process machine and a device for realizing said method - Google Patents

Abstract

FIELD: machine building.

SUBSTANCE: invention relates to application of process vibration machines. Method of changing and adjusting the dynamic state of a vibration process machine includes excitation of oscillations of the working member of the vibration process machine and recording displacement of the coordinates of movement of the vibration process machine. According to the first invention, oscillations amplitudes of the extreme points of the vibration machine are recorded, the information obtained from the dynamic state monitoring sensors is transmitted to the control unit, adjusting the ratio between these amplitudes until obtaining a mode of synchronous operation in two coordinates, wherein the ratio is adjusted by changing the given stiffness of the system. Device for realizing the method of adjusting and changing the dynamic state of a process machine consists of a working member, elastic links hinged to the working member and a support surface, as well as a control unit and working member vibration state monitoring sensors. According to the second invention, the device is equipped with additional links in the form of two lever mechanisms, which contain paired pivotally connected rods, equipped in the connection point of the rods of each pair by a load, and gear sectors installed on the lower ends of rods located at the bottom, at that toothed sectors are connected with toothed blocks and brake shoes interacting with cylindrical surfaces of toothed blocks to influence motion of toothed sectors.

EFFECT: method for changing and adjusting the dynamic state of a vibration process machine and a device for realizing said method are disclosed.

2 cl, 3 dwg

Description

The invention relates to the field of improving the reliability and operating efficiency of engineering facilities related to technological vibratory machines. Machines of this kind are widely used in mining, construction and chemical industries. The features of such machines are described in sufficient detail in the scientific literature.

Vibration technological machines implement a wide range of processes of vibration transportation of parts and bulk working mixtures, are used in the classification of separation of various materials, and also in the implementation of processing processes and modification of the properties of surfaces of parts during vibration hardening of parts, their cleaning from traces of previous processing processes, etc.

Productivity and quality of vibratory technological processes essentially depends on the dynamic state of working bodies. First of all, this is due to the possibility of forming the structure of the vibration field, the distribution of the vibration amplitudes of individual points of the working body along its length. Of great importance, in connection with this, are the opportunities to change the dynamic states of working bodies, to adjust and adjust the local dynamic properties of vibrating technological machines. In many cases, the necessary conditions for adjusting and adjusting the dynamic states of technical objects are achieved by introducing additional connections into the structure of systems, including in the form of various mechanisms and devices for converting motion, etc.

In the process of patent search revealed a number of inventions analogues.

Known invention [Kucherov A.A. “Vibrating stand with balancing mechanism”, patent No. 82850 U1, IPC G01M 7/02, priority 05/10/2009], which is a vibrating stand with a balancing mechanism, containing a base on which vertical posts are connected, connected in the upper part by a crossbar, an oscillation generator and a load a device in the form of a desktop and a table extender attached to it, characterized in that the table extender of the load device is made in the form of a box-shaped volumetric structure with a flat upper surface, in which are balanced a mechanism consisting of a disk that can be rotated in a horizontal plane, with a smaller diameter eccentrically located disk in it, also that can be rotated in a horizontal plane, and an adjusting screw eccentrically mounted in a disk of a smaller diameter so that everything assembled with the test items is loaded the device has the ability to hang on this screw by rotating it above the upper supporting plane of the table and move in a horizontal plane relative to the center p the working table by mutual rotation of the disks of the balancing mechanism relative to each other until the centers of gravity of the load device and the working table are placed on the same vertical, then again lower down onto the expander and firmly fix on it.

The disadvantages of this invention include the lack of a mathematical description of the proposed technical solution and the absence of a regulatory mechanism.

Electromechanical test shaker is also known [Bugayets A.I., Kravchenko A.F., Potaenko E.N., Chilikov S.M., Tabunchikov A.V. "Electromechanical test vibrostand", patent No. 2419078 C2, IPC G01M 7/06, priority 01/20/2011], comprising a base, a table, movably coupled to the base with guides providing vertical movement of the table, an electric motor with an eccentric mechanism on which the table rests, return springs providing constant contact of the table with the eccentric mechanism, a drive and measurement unit and a vibration sensor, characterized in that the table guides are made in the form of two identical four-link parallelograms, plane and which are parallel to the axis of movement of the table, while the parallelogram links of the same name are made in the form of elastic pliable plates in the direction of movement of the table and pairwise mounted on the base of the vibrating table and on the table so that in the neutral mid-position of the table adjacent parallel links of the parallelograms are in a horizontal parallel plane of the table position. The eccentric mechanism mounted on the motor shaft is made with the possibility of controlling the eccentricity and, accordingly, the amplitude of the table vibration.

The main disadvantages of the analogue under consideration are the lack of mathematical modeling of the processes that occur during the operation of the installation, as well as the lack of inattention to the modes of coordinated movement of coordinates of the extreme points of the object.

The invention is known [Rumyantsev Yu.S., Ananyin I.K., Galyapin D.V. “Installation for vibration-shock treatment of surfaces of thin-walled parts”, Patent No. 63281 U1, IPC ВВВ 31/06, priority 05/27/2007], which is an installation for vibration-shock processing of surfaces of thin-walled parts, containing a container for accommodating workpieces together with abrasive filler mounted on an elastically mounted frame carrying inertial vibrators with shafts connected to a rotation drive and arranged in two rows under the container on both sides of its center of gravity, characterized in that the sleep container It is equipped with a device for positioning and securing the workpiece, which is self-locking at a given processing angle and made in the form of a rigid frame equipped with trunnions located along both ends of the axis of rotation mounted in bearings of split lunettes mounted on the side walls of the container and with stops interacting with the rearranged pins that set the angle of the frame for different directions of rotation of the vibrator shafts and are installed in the radial cutouts of the plates mounted on the lunettes.

The disadvantages of this invention are the lack of regulation of the reduced rigidity of the system, as well as inattention to the mathematical description of the processes that occur during operation of the installation.

The prototype is a method of controlling the amplitude when automatically tuning to the resonant mode of vibration of a vibrating machine driven by an induction motor [Panovko G.Ya., Shokhin A.E., Barmina O.V., Eremeykin S.A. "The method of controlling the amplitude when automatically tuning to the resonant mode of vibration of a vibrating machine driven by an induction motor", Patent No. 2653961 C1, IPC B06B 1/14, priority 05/15/2018], which consists in the fact that the vibrations of the working body of a vibrating machine with a damper with With prescribed dissipative characteristics, they are excited by periodic force due to the unbalance of the inertial vibration exciter driven by an induction motor, the rotation frequency of which is tuned to the resonant mode of oscillations of the mechanical system we use a vibration machine according to a given algorithm, for which we simultaneously measure the movement of the working body and the angular position of the unbalance, characterized in that it measures the mismatch of the amplitude of the vibrations of the working body with its predetermined value, changes the magnitude of the dissipation of vibration energy in the damper, reducing the magnitude of the mismatch of the vibration amplitude the working body to zero, while the change in the magnitude of the dissipation is calculated according to a predetermined algorithm that relates the amplitude of the oscillations of the working body and dissipative damper characteristics.

The main disadvantage of this invention is the inability to control the reduced stiffness of the system. The disadvantages also include the lack of a mathematical description of the vibration modes.

The objective of the invention is the control of the dynamic state of the vibrating technological machine by adjusting the length of the lever arm.

A method for changing and adjusting the dynamic state of a vibrating technological machine, including excitation of vibrations of the working body of the vibrating technological machine and recording the displacements of the motion coordinates of the vibrating technological machine, characterized in that the oscillation amplitudes of the extreme points of the vibrating machine are recorded, the information received from the sensors for monitoring the dynamic state goes to the control unit , adjust the ratio between these amplitudes to obtain the mode of their synchronous operation for d mind coordinates, wherein the ratio is adjusted by changing the stiffness of the system shown

A device for implementing the method of adjusting and changing the dynamic state of a technological machine, consisting of lever mechanisms and additional connections operating in the conditions of steady-state oscillatory movements, characterized in that the values of reduced mass inertial parameters are created not only by the passive method, but also by creating effects of changing the reduced mass inertial elements systems arising from the effects of the transformation of movements by additional bonds created by specially introduced mechanics nism for converting the movement and the brake pads affecting the movement of toothed sectors.

The essence of the invention is illustrated by drawings.

In FIG. 1 shows a schematic diagram of a vibrating technological machine with devices for changing and adjusting the dynamic state, comprising a supporting surface 1, a working body 2, elastic elements 3, 4, rods 5, 6, 7, 8, gear sectors 9, 10, weights 11, 12 , gear blocks 13, 14, brake pads 15, 16, pneumatic actuators 17, 18, control unit 19, vibration monitoring sensors 20, 21, vibration exciters 22, 23, wiring 24, 25.

In FIG. 2 shows the design diagram of a vibrating technological machine with additional connections, composed according to FIG. 1.

In FIG. 3 shows a structural mathematical model (block diagram) of the original system of the technological vibration machine of FIG. 2.

The invention works as follows.

The present invention is a mechanical oscillating system, consisting of a working body 2 in the form of a solid body resting on elastic surface 1 through elastic elements 3, 4. Such a mechanical oscillating system is a design scheme of a technological vibrating machine (vibration stand) with two degrees of freedom.

The working body 2 of the vibrating machine has two elastic elements 3 and 4, which are springs that are pivotally mounted in TT. (A) and (B) on the supporting surface 1; two tt. (A ₁ ) and (B ₁ ) the elastic elements 3, 4 are pivotally fixed to the working body 2. In addition to the elastic connections in the system, implemented by the springs 3 and 4, additional connections are introduced and used in the form of two linkage mechanisms. These mechanisms consist respectively of the rods 5, 6 and the gear sector 9, as well as the rods 7, 8 and the gear sector 10. In this case, the link 9 is a gear sector of radius R ₁ connecting to the gear block 13.

In vols. (A ₀ ) and (B ₀ ) the weights 11 and 12 are located. The weights of these weights can change during the setup process. The working body 2 as a solid, has a mass M and a moment of inertia J. The center of mass of the system is located in t. (O); its position is determined respectively by the lengths l ₁ -A ₁ O, l ₂ = B ₁ O.

The movement of the working body 2 is described in two coordinate systems at ₁ , ₂ , and also at ₀ , ϕ, associated with a fixed basis, initiated by vibration exciters 22, 23. The position of the links of the lever mechanisms or devices for converting movement is determined by the angles α ₁ , β ₁ and α ₂ , β ₂ .

, и стержня 8 со стороной

, который присоединяется к зубчатого сектора 10. Зубчатый сектор 10 имеет радиус R₂. Зубчатый сектор соединяется с зубчатым блоком 14, имеющим радиус r₂; к цилиндрической поверхности блока могут прижиматься тормозные колодки 15, 16, что создает при взаимодействиях элементов определенные силы сопротивления. В первом приближении, момент сил сопротивления может интерпретироваться как введение в систему дополнительной связи, реализующей эффект увеличения приведенной массы. Режим управления при настройке осуществляется приводами 17, 18 с питанием от блока управления 19 (например, ресивер).In t. (B ₁ ) additional links in the form of lever mechanisms having levers in the form of rods 5, 7 in length are attached to the working body 2 at the edges

, and rod 8 with side

which is attached to the gear sector 10. The gear sector 10 has a radius R ₂ . The gear sector is connected to the gear block 14 having a radius r ₂ ; brake pads 15, 16 can be pressed against the cylindrical surface of the block, which creates certain resistance forces during element interactions. In a first approximation, the moment of resistance forces can be interpreted as the introduction of an additional bond into the system that realizes the effect of increasing the reduced mass. The control mode during configuration is carried out by the drives 17, 18 powered by the control unit 19 (for example, the receiver).

The system works in such a way that the parameters of the dynamic state, which must be maintained during a certain working technological cycle, are pre-configured on the basis of a special device; such a device has sensors for monitoring the vibrational state 20, 21 according to the coordinates of the working body. This information is processed in the control unit 19 and determines the value to press on the brake pads 15 and 16. The sensors are connected to the control unit 19 through the wiring 24, 25. The pads are driven by pneumatic actuators 17, 18; by using a throttle (control unit 19). The system has a compressor to create overpressure.

The control system is simple and designed to service vibrating technological processes with long technological cycles. The system has the capabilities of detailed tuning actions and corrections when changing the given mass inertia parameters, by changing also the masses of the weights 11 and 12.

Theoretical basis of the technology for changing the dynamic state of a technological vibrating machine

The design diagram of a technological vibration machine, the dynamic state of which can be changed by introducing additional bonds, is presented in the form of a mechanical oscillatory system with two degrees of freedom, as shown in FIG. 2.

The working body of the machine is a solid body that performs plane motion in the coordinate systems y ₁ , y ₂ and y ₀ , ϕ in a fixed basis.

In studies of the dynamic state of the system of FIG. 2 it is assumed that the system has linear properties and performs small fluctuations with respect to the position of static equilibrium, which is also determined by the values of the angles α ₁ , α ₂ , β ₁ and β ₂ that determine the initial configuration of the contour of the lever (rod) links.

и

с радиусами r₁ и r₂ соответственно. К элементам

и

приложены моменты сил сопротивления М₁ и М₂, создаваемые специальными тормозными устройствами.In the process of movement of the working body, elastic reaction forces (or reactions) are formed in volts. (A), (A ₁ ), (B), (B ₁ ), this causes dynamic interactions of elements of the system of additional bonds. Additional bonds are made in the form of gear sectors with radii R ₁ and R _2, respectively. These gear sectors have moments of inertia J ₁ and J ₂ , which mesh with special gear units having moments of inertia

and

with radii r ₁ and r ₂ respectively. To items

and

applied moments of resistance forces M ₁ and M ₂ created by special braking devices.

The movements of the working body also cause the corresponding movements of the additional masses (weights) m ₁ and m _2, respectively, which affects the distribution of the amplitudes of oscillations of the points of the working body. The set of motion parameters of the points of an oscillating solid with mass M and moment of inertia J determines the parameters of the vibration field of the working body.

,

,

,

, соответственно.The center of mass of the system is located in t. (O), defined by the lengths l ₁ and l ₂ . Additional connections are realized by link mechanisms with link lengths

,

,

,

, respectively.

1. To construct mathematical models of the system, a technology is used that is determined by the Lagrange formalism of the second kind, which is described in sufficient detail, for example, in [1, 2]. It is believed that between the coordinates y ₁ , y ₂ and y ₀ , ϕ there are relations:

Where

To build a mathematical model of the system, we can write expressions for the kinetic and potential energies of the system shown in Fig. 1:

- абсолютные скорости движения точек (A₀), (В₀) - расположения сосредоточенных масс m₁ и m₂ соответственно; ε₁, ε₂ - угловые скорости зубчатых секторов

a₁, а₂, b₁, b₂ - коэффициенты, зависящие от параметров дополнительных связей

. Все коэффициенты определяются на основе кинематических расчетов.here

- the absolute speed of the points (A ₀ ), (B ₀ ) - the location of the concentrated masses m ₁ and m _2, respectively; ε ₁ , ε ₂ - the angular velocity of the gear sectors

a ₁ , a ₂ , b ₁ , b ₂ - coefficients depending on the parameters of additional bonds

. All coefficients are determined based on kinematic calculations.

The system of equations in the time domain has the form:

In the time domain, the mathematical model of the original system (Fig. 1) is a system of two linear ordinary second-order differential equations with constant coefficients. External influences Q ₁ (t) and Q ₂ (t) are in-phase harmonic functions. Practically, such external factors are realized in the simplest form using vibration exciters, for example, inertial ones, which is described in sufficient detail in [3]. To expand the possibilities of correcting vibration fields and changing the dynamic states of the working body, certain advantages are the ability to create conditions under which there is a coherence of external factors:

where α is the coefficient of connectivity of two external influences, α can take zero, positive and negative values; for α = 1, the case considered in Fig. 1.

2. The system of equations (5), (6) based on the Laplace transforms under zero initial conditions can be transformed into the system of equations in operator form

значок 〈-〉 над переменной означает ее изображение по Лапласу [1]. Система уравнений в операторной форме может быть представлена в виде структурной математической модели или структурной схемы эквивалентной в динамическом отношении системы автоматического управления.where p = jω is the complex variable

the 〈-〉 icon above a variable means its Laplace image [1]. The system of equations in operator form can be represented in the form of a structural mathematical model or structural diagram of a dynamically equivalent automatic control system.

3. Using the block diagram of FIG. 3, we write down the transfer functions necessary for solving the problem of correction and formation of the vibration field:

Where

- frequency characteristic equation of the system.

4. To configure and change the dynamic state of the system, it is proposed to use the inter-partial transfer function W ₁₂ (p) defined by expression (13).

, то из (12) можно найти частоту вибрационного воздействия, при которой такое заданное однородное вибрационное поле формируется. Если получаемая частота для получения такого поля не соответствует регламенту технологического процесса, то определение подходящего значения частоты или частотного диапазона, может быть обеспечено путем выбора изменяемых параметров. Такими парметрами могут быть величины пригрузов m₁ и m₂, закрепляемых в тт. (А₀), (В₀).If you ask

, then from (12) it is possible to find the frequency of the vibrational impact at which such a given uniform vibrational field is formed. If the obtained frequency for obtaining such a field does not comply with the technological process regulations, then the determination of a suitable frequency value or frequency range can be achieved by selecting variable parameters. Such parameters can be the values of the loads m ₁ and m ₂ , fixed in TT. (A ₀ ), (B ₀ ).

и

При увеличении М₁ и М₂ происходит соответствующее по своей физической значимости изменение приведенных моментов инерции. По существу, коррекция и изменение динамического состояния вибростенда с позиций изменения приведенных моментов инерции дополнительных связей осуществляется через использование соотношения, когда выполняется условие

и

Здесь M₁ и М₂ являются моментами сил сопротивления, формируемыми специальным устройством, обеспечивающим прижатие тормозной колодки к ободу специальной цилиндрической накладки на том же валу, что и зубчатое колесо с моментом инерции

и

Настройка вибрационного поля и динамического состояния вибрационного технологического стенда осуществляется на предварительной стадии подготовки технологического комплекса к работе. Для настройки могут производиться также предварительные расчеты с учетом конкретных упругих, массоинерционных параметров системы, а также ее геометрических характеристик. Структура поля, формы распределения амплитуд колебаний рабочего органа задаются на основе передаточной функции межпарциальной связи. Предлагаемый подход допускает возможности полной автоматизации настройки и коррекции вибрационного состояния. При формировании методики расчета используются следующие литературыThe variable parameter can be the coefficient of connectivity of the vibration effects a, which accordingly requires certain structural and technical solutions in the blocks of vibrational excitation of the vibrating stand. As a tuning parameter, a change in the braking moments M ₁ and M _{2 is} proposed, which transforms into a corresponding change in the reduced moment of inertia

and

With an increase in M ₁ and M ₂ , a change in the given moments of inertia corresponding in its physical significance occurs. Essentially, the correction and change in the dynamic state of the vibration bench from the position of changing the given moments of inertia of the additional bonds is carried out through the use of the ratio when the condition

and

Here, M ₁ and M ₂ are the moments of resistance forces formed by a special device that ensures that the brake shoe is pressed against the rim of a special cylindrical lining on the same shaft as the gear wheel with the moment of inertia

and

The setting of the vibration field and the dynamic state of the vibration technological stand is carried out at the preliminary stage of preparation of the technological complex for work. For tuning, preliminary calculations can also be made taking into account specific elastic, mass inertia parameters of the system, as well as its geometric characteristics. The structure of the field, the shape of the distribution of the amplitudes of the oscillations of the working body are set on the basis of the transfer function of the inter-partial communication. The proposed approach allows the full automation of tuning and correction of the vibrational state. In the formation of the calculation methodology, the following literature is used

1. Bykhovsky II. Fundamentals of the theory of vibration technology / II. Bykhovsky. - M.: Mechanical Engineering, 1968 .-- 362 p.

2. Eliseev S.V. Applied theory of oscillations in problems of the dynamics of linear mechanical systems / S.V. Eliseev, A.I. Artyunin. - Novosibirsk: Nauka, 2016 .-- 459 p.

3. Eliseev S.V. Applied system analysis and structural mathematical modeling / S.V. Eliseev. - Irkutsk: IrGUPS, 2018.

Claims (2)

1. A method of changing and adjusting the dynamic state of a vibrating technological machine, including excitation of vibrations of the working body of the vibrating technological machine and recording the displacements of the motion coordinates of the vibrating technological machine, characterized in that the vibration amplitudes of the extreme points of the vibrating machine are recorded, the information received from the sensors for monitoring the dynamic state goes to control unit, adjust the ratio between these amplitudes to obtain the mode of their synchronous operation by two coordinates, and adjust the ratio by changing the reduced stiffness of the system 2. A device for implementing a method of adjusting and changing the dynamic state of a technological machine, consisting of a working body, elastic ties pivotally attached to a working body and a supporting surface, a control unit and sensors for monitoring the vibrational state of the working body, characterized in that it is provided with additional connections in in the form of two lever mechanisms that contain pairwise articulated rods equipped with a load at the junction of the rods of each pair, and gear sectors installed and lower ends of the rods located at the bottom, with toothed sectors associated with the gear units and brake pads which interact with the cylindrical surfaces of the toothed blocks to effect movement of the toothed sectors.

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