RU2741748C1 - Method for excitation of mechanical oscillations of power factors with controlled parameters - Google Patents

Abstract

FIELD: physics.SUBSTANCE: invention relates to vibration equipment, particularly to agroindustrial complex, and can be used for grain processing enterprises in the process and transport equipment. According to the invention, in four-debalance-type vibration exciter, which excites oscillation of power factors by asymmetric law, change of direction of maximum power factor by absolute value to opposite one is achieved by changing initial position of slow-rotating unbalances.EFFECT: technical result is a variation in the speed of transportation and higher efficiency of separation of grain mixtures.1 cl, 22 dwg

Description

The invention relates to vibration technology, in particular to the technology of the agro-industrial complex, and can be used at grain processing plants in technological and transport equipment. In addition, the invention can be used in other industries related to the processing of bulk materials.

The purpose of the invention is to expand the functionality of the centrifugal vibration exciter when used in vibration equipment for separation and transportation of grain and other bulk materials, by communicating vibrations to the working bodies of machines with parameters corresponding to the process being carried out.

Known methods of excitation of mechanical vibrations of force factors (force and / or moment) using centrifugal vibration exciters. In this case, the vibration exciter may contain one or several unbalances. An unbalance is a rotating unbalanced link. The unbalance imbalance is the product of the unbalanced mass m by its eccentricity r relative to the axis of rotation.

The known method of excitation of non-harmonic (obeying an asymmetric law) oscillations of the force [1] centrifugal vibration exciter containing four unbalances, uniformly rotating around parallel axes (Fig. 1). The unbalance axes of rotation are located on a common base. The unbalances in pairs have the same angular velocities in the opposite direction. In this case, the value of the angular velocity of the first pair of unbalances is half the value of the angular velocity of the second pair of unbalances, that is, the first pair of unbalances rotates with an angular velocity ω ₁ = ω, and the second with an angular velocity - ω ₂ = 2ω. Unbalances rotating with equal angular velocities have the same unbalances, that is, the same magnitude product of the unbalanced mass m and its eccentricity r relative to the axis of rotation. Moreover, imbalances of unbalances rotating with a frequency of 2ω are four times less than the value of unbalances of unbalances rotating with a frequency of ω. To simplify further reasoning, we will agree to call the unbalances of the same name, rotating with equal angular velocities, and the segment connecting the axes of rotation of such unbalances, the center distance of the unbalances of the same name. The axes of rotation of the unbalances of the same name are located symmetrically with respect to a straight line perpendicular to their center-to-center distance. In this case, the axes of rotation of the first pair of unbalances and the axes of rotation of the second pair of unbalances are located symmetrically relative to one straight line.

- центробежная сила инерции, развиваемая дебалансом первой пары;

- центробежная сила инерции, развиваемая дебалансом второй пары. На рисунке (фиг. 2) показано некоторое произвольное положение дебалансов после поворота из начального положения первой пары дебалансов на угол δ₁=δ, второй пары - на угол δ₂=2δ. Как видно из рисунка, горизонтальные составляющие сил инерции одноименных дебалансов взаимно уравновешивают друг друга. Вертикальные составляющие сил инерции дебалансов складываясь, образуют результирующую силу, зависимость которой от угла поворота дебалансов имеет видLet us explain the principle of operation of such a centrifugal vibration exciter. With uniform rotation of unbalances, centrifugal forces of inertia develop:

- centrifugal force of inertia, developed by the unbalance of the first pair;

is the centrifugal force of inertia developed by the unbalance of the second pair. The figure (Fig. 2) shows some arbitrary position of the unbalances after turning from the initial position of the first pair of unbalances through the angle δ ₁ = δ, the second pair - through the angle δ ₂ = 2δ. As can be seen from the figure, the horizontal components of the inertia forces of the unbalances of the same name mutually balance each other. The vertical components of the unbalance inertia forces, adding up, form a resultant force, the dependence of which on the unbalance rotation angle has the form

directed along a straight line, which is the axis of symmetry of the arrangement of the axes of rotation of the unbalances.

The dependence of the resulting force on the angle of rotation of the unbalances, described by Eq. (1), was obtained under the condition that the initial position of the unbalances was taken to be such a position in which the centrifugal forces of inertia of the first and second pairs of unbalances simultaneously create the maximum resultant forces of the same direction. The resultant centrifugal forces of inertia of the first and second pairs of unbalances in the initial position are respectively equal to P _P1 = 2m ₁ r ₁ ω ² and P _P2 = 8m ₂ r ₂ ω ² . Obviously, in this case, in the initial position of the unbalances, the vibration exciter excites the maximum possible force.

As noted above, the imbalance of rapidly rotating unbalances is four times less than the imbalance of slowly rotating unbalances, that is, if the imbalance of the slowly rotating unbalance is m ₁ r ₁ = mr, then the imbalance of the rapidly rotating unbalance is m ₂ r ₂ = 0.25 mr. Then the resulting force excited by the vibration exciter has the form

The dependence of the resulting force excited by the vibration exciter in dimensionless expression can be represented as

The figure (Fig. 3) shows a graph of the dependence of the resulting force in dimensionless expression on the angle of rotation of the unbalances for the cycle of the vibration exciter mechanism. Note that the cycle of the vibration exciter mechanism is the time after which the unbalances return to the initial (initial) position. In the case under consideration, during the kinematic cycle, slowly rotating unbalances make one revolution, and rapidly rotating ones - two.

As can be seen from the graph (Fig. 3), the function of the resulting force from the angle of rotation of the unbalances has the largest value equal to two, and the smallest - minus one point one hundred twenty five thousandths. This means that the maximum values of the force excited by the vibration exciter in opposite directions are not equal to each other. With the adopted positive and negative directions of force, the absolute value of the maximum value of the resultant force in the positive direction is greater than the absolute value of the maximum value of the force in the negative direction, that is, there is an asymmetry in the law of oscillations of the force excited by the vibration exciter.

It should be noted that the force developed by such a vibration exciter is capable of imparting rectilinear nonharmonic vibrations to the base and the associated working body if the force passes through the center of mass of the vibrating system. Inharmonicity of the law of oscillations in this case means the inequality of the largest positive value of the acceleration of the working body to the absolute value of the largest negative value of acceleration.

This method of excitation of force oscillations is implemented in the design of machines in order to communicate to the working body nonharmonic (asymmetric) rectilinear oscillations.

The known method of excitation of non-harmonic oscillations of the moment [2] centrifugal vibration exciter, containing four unbalances rotating around parallel axes (Fig. 4). The unbalance axes of rotation are located on a common base. The unbalances rotate uniformly, in pairs they have the same angular velocity and direction and the same unbalances. The rotation of the unbalances is synchronized and phase-matched so that the unbalances of the same name simultaneously occupy positions in which the centrifugal forces of inertia developed by them are parallel to each other and directed in opposite directions. Consequently, the centrifugal forces of inertia of the unbalances of the same name create a pair of forces, the moment of which is variable in magnitude and direction, and its magnitude and direction depend on the position of the unbalances.

The figure (Fig. 5) shows an arbitrary position of the unbalances: the unbalances of the first pair, rotating with an angular velocity ω ₁ = ω, are shown when they are rotated from the initial position through the angle δ ₁ = δ; the unbalances of the second pair, rotating with an angular velocity ω ₂ = 2ω, are shown when they are rotated from the initial position through an angle δ ₂ = 2δ. Let's consider the counterclockwise moment as positive. As can be seen from the figure (Fig. 5), in the considered position, the inertial forces of the first and second pairs of unbalances form pairs of forces, the moments of which are positive. The moment of the pair, created by the inertial forces of slowly rotating unbalances, is equal to М ₁ = 2l ₁ m ₁ r ₁ ω ² cosδ. The moment of the pair, created by the inertial forces of rapidly rotating unbalances, is equal to М ₂ = 8l ₂ m ₂ r ₂ ω ² cos2δ. The resulting moment excited by the vibration exciter is equal to the algebraic sum of the moments created by the centrifugal forces of inertia of the first and second pairs of unbalances. The dependence of the resulting torque on the angle of rotation of the unbalances has the form

From the analysis of equation (4), the following conclusions can be drawn. The dependence of the resulting moment is subject to an inharmonic law. The dependence of the resulting moment, described by equation (4), takes place under the condition: in the initial position of the unbalances, the centrifugal forces of inertia of the unbalanced unbalances create the maximum moments of the same (positive) direction. This initial position of the unbalances can be characterized as follows: the centrifugal forces of inertia of the unbalances of the same name are directed perpendicularly to the straight lines connecting the axes of their rotation, in opposite directions.

The resulting moment excited by such a vibration exciter can impart to the base, and, consequently, to the associated working body of the machine, either inharmonic rotational vibrations, or rotational vibrational motion (rotation with rotational vibrations superimposed on it).

If the imbalance of the rapidly rotating unbalance is four times less than the imbalance of the slowly rotating unbalance and the distance between the axes of rotation of the first and second pairs of unbalances are equal to each other 2l ₁ = 2l ₂ = 2l, then the dependence of the moment excited by the vibration exciter will have the form

The dependence of the moment excited by the vibration exciter in dimensionless expression can be represented as

При этом за начальное положение дебалансов принято положение, в котором силы инерции одноименных дебалансов создают максимальные по величине силовые факторы (силы или моменты) одинакового направления. Легко убедиться, что при одинаковых соотношениях максимальных значений силовых факторов, возбуждаемых силами инерции медленно и быстровращающихся дебалансов, и при одинаковых условиях начальной фазировки дебалансов, законы колебаний силы и момента в безразмерном выражении будут иметь как одинаковый характер, так и одинаковые параметры колебаний.As you can see, the right-hand sides of equations (3) and (6) have the same form. Consequently, the fluctuations of force and moment obey the same law. Note that the dependences of the resulting force and moment, described respectively by equations (3) and (6), correspond to such setting parameters (masses m ₁ and m ₂ , eccentricities r ₁ and r ₂ , distances between the axes of rotation of the same unbalances 2l ₁ and 2l ₂ ) vibration exciter, at which the ratio of the maximum values of the force factors excited by the inertial forces of slowly and rapidly rotating unbalances is equal to unity, that is, at

In this case, for the initial position of the unbalances, a position is taken in which the inertial forces of the unbalanced unbalances create the maximum force factors (forces or moments) of the same direction. It is easy to verify that with the same ratios of the maximum values of the force factors excited by the inertial forces of slowly and rapidly rotating unbalances, and under the same conditions for the initial phasing of the unbalances, the laws of force and moment oscillations in dimensionless expression will have both the same character and the same oscillation parameters.

Consequently, a four-balance vibration exciter, depending on the conditions of phasing of the same unbalances and the directions of their rotation relative to each other (in one direction or in opposite directions), can excite oscillations of either force or moment obeying an inharmonic law. Moreover, the laws have the same characteristics (symmetric, asymmetric law, the degree of asymmetry of the vibration law) with the same ratios of the maximum value of the force factor (force or moment) excited by the inertial forces of slowly rotating unbalances to the maximum value of the force factor excited by the inertial forces of rapidly rotating unbalances, and under the same conditions initial phasing of unbalances.

. Дебалансы, вращающиеся с равными по величине угловыми скоростями, имеют одинаковые массы m и эксцентриситеты r относительно оси вращения. Оси вращения одноименных дебалансов, вращающихся с одинаковыми по величине угловыми скоростями, расположены симметрично относительно прямой, перпендикулярной их межосевому расстоянию. При этом оси вращения первой пары дебалансов и оси вращения второй пары дебалансов расположены симметрично относительно одной и той же прямой.The closest in technical essence and the achieved result is a method of excitation of mechanical vibrations of force factors with predicted parameters [3] by a centrifugal vibration exciter containing four unbalances rotating around parallel axes. The unbalance axes of rotation are located on a common base. The unbalances rotate uniformly and have the same angular velocities in pairs. In this case, the value of the angular velocity of the first pair of unbalances is less than the value of the angular velocity of the second pair of unbalances. The first pair of unbalances rotates with an angular velocity ω ₁ = ω, and the second with an angular velocity ω ₂ = nω, where n is the gear ratio of the transmission that synchronizes and phase-matches the rotation of the unbalances, which is equal to the ratio of the angular velocity of rapidly rotating unbalances to the angular velocity of slowly rotating

... Debalances rotating with equal angular velocities have the same masses m and eccentricities r relative to the rotation axis. The axes of rotation of the same unbalance, rotating with the same magnitude of angular velocities, are located symmetrically relative to a straight line perpendicular to their center distance. In this case, the axes of rotation of the first pair of unbalances and the axis of rotation of the second pair of unbalances are located symmetrically relative to the same straight line.

The figure (Fig. 6) shows a vibration exciter containing four unbalances, designed to excite inharmonic oscillations of the force provided that the centrifugal forces of inertia of the first and second pairs of unbalances in the initial position develop maximum forces of the same direction.

The dependence of the force excited by such a vibration exciter has the form

The dependence of the excited force in dimensionless expression can be represented as

- коэффициент, равный отношению максимального значения силы, создаваемой силами инерции медленновращающихся дебалансов, к максимальному значению силы, создаваемой силами инерции быстровращающихся дебалансов.Where

- a coefficient equal to the ratio of the maximum value of the force created by the inertial forces of slowly rotating unbalances to the maximum value of the force created by the inertial forces of the rapidly rotating unbalances.

The figure (Fig. 7) shows a vibration exciter containing four unbalances, designed to excite inharmonic oscillations of the moment, provided that the centrifugal forces of inertia of the first and second pairs of unbalances in the initial position develop maximum moments of the same direction.

The dependence of the moment excited by this vibration exciter has the form

The dependence of the excited moment in dimensionless expression can be represented as

- коэффициент, равный отношению максимального значения момента, создаваемого силами инерции медленновращающихся дебалансов, к максимальному значению момента, создаваемого силами инерции быстровращающихся дебалансов.Where

- coefficient equal to the ratio of the maximum value of the moment created by the forces of inertia of slowly rotating unbalances to the maximum value of the moment created by the forces of inertia of rapidly rotating unbalances.

As you can see, the right-hand sides of equations (8) and (10) completely coincide when the coefficients are equal a = b. Consequently, the laws of oscillation of force and moment, excited by a four-balance vibration exciter, have the same characteristics with the same ratio of the maximum values of the force factors created by the forces of inertia of slowly and rapidly rotating unbalances.

Such a four-balance vibration exciter, depending on the initial phasing of the unbalances and the magnitude of the gear ratio of the transmission, synchronizing and phase-matching the rotation of the unbalances, can create fluctuations in force factors (force or moment) obeying either an asymmetric or symmetric law. The vibration exciter excites asymmetric oscillations of force factors (force or moment) if the following conditions are simultaneously met. In the initial position, the centrifugal forces of inertia of slow and rapidly rotating unbalances create maximum force factors. The sum of the total numbers of revolutions of the unbalances of the first and second pairs when they are simultaneously returned to their initial position, that is, for the kinematic cycle of the vibration exciter mechanism, is an odd number. Obviously, the second condition is fulfilled at certain values of the gear ratio of the gear synchronizing and phase matching the rotation of the unbalances. The second condition is satisfied if the gear ratio n of the gear synchronizing and phase matching the rotation of the unbalances is a fractional number consisting of an integer part that is an even number and a fractional part equal to four tenths. That is, the gear ratio n is a fractional number of the form n = i + 0.4, where i is an even number. Such a fractional number can be characterized as follows: a fractional number, when multiplied by five, we get an even number - 5n = 5i + 2. With this value of the gear ratio of the transmission, synchronizing and phase matching the rotation of the unbalances, in the four-balance centrifugal vibration exciter, during the kinematic cycle of the vibration exciter mechanism, the slow-rotating unbalances make five revolutions, and the number of full revolutions of the rapidly rotating unbalances is equal to an even number equal to the five-fold ratio of the transmission value n. Consequently, with such values of the gear ratio n, the sum of the total numbers of revolutions of the unbalances when they are simultaneously returned to their initial position is an odd number. The vibration exciter excites symmetric oscillations of the force factors when one of the following conditions is met. In the initial position, the centrifugal forces of inertia of slowly and rapidly rotating unbalances create force factors equal to zero. The sum of the total numbers of revolutions of the unbalances of the first and second pairs for the kinematic cycle is an even number. Note that in this initial position of the unbalances, the centrifugal forces of inertia of the unbalances of the same name are directed along the straight line connecting the axes of their rotation in opposite directions and balance each other.

The implementation of this method of excitation of mechanical vibrations of force factors with predicted parameters in the drives of vibration technological and transport equipment for processing grain and other bulk materials allows communicating vibrations with different parameters of the law of motion to the working bodies of machines. That is, to create a drive that allows you to provide the parameters of the oscillation law of the working body in accordance with the process carried out in the equipment. However, such a drive has one significant drawback: a limited range of variation of the parameters of the law of oscillation of force factors.

So, to change to the opposite direction of the force factor with the largest value in modulus, that is, to change the direction of asymmetry of the law of oscillations of the force factor, the position of the vibration exciter must be changed. The exciter must be rotated 180 ° relative to its original position. If it is necessary to change the position of the vibration exciter, first dismantle the vibration exciter, and then install and adjust it in a new position. In this case, such a permutation of the vibration exciter must be provided for by the design of the machine.

Consequently, the use of known methods of communicating motion to the working bodies of machines according to the laws, the parameters of which correspond to the type of the process carried out in the equipment, is accompanied by the complication of the drive design, as well as the creation of various designs of drive mechanisms.

The implementation of the proposed method for regulating the parameters of the laws of fluctuations of force factors in the designs of equipment for processing grain and other bulk materials will create a unified drive, in which a change in the initial position of slowly rotating unbalances provides a change to the opposite direction of the force factor with the highest modulus value.

It is known that the reason for the directional average movement of particles of a granular body along a horizontal uniformly rough surface that performs horizontal oscillations is the asymmetry of the surface oscillation law, which is expressed in the fact that the greatest value of the acceleration of the supporting surface in one of the directions differs in absolute value from the greatest value of acceleration in the opposite direction. The value of the average speed of transportation of particles of a granular body relative to an oscillating surface with other conditions being the same (frequency of oscillations of the support surface, coefficients of resistance to shear of particles relative to the surface) depends on how much the largest positive value of the surface acceleration differs in magnitude from the largest negative acceleration. The direction of the average conveying speed depends on the modulus of which of the two highest values of the plane acceleration is greater - positive or negative.

The average speed of vibration is the main parameter that determines the productivity of the transport equipment, and in the separation equipment - the productivity and efficiency of the process carried out in this equipment. The average speed of vibration movement affects the efficiency of the separation process through the thickness of the layer of bulk material and the time it remains on the working body. With a constant length of the working surface (for example, the length of the sieve), an increase in the average speed of the bulk body reduces the time of the separation process and the thickness of the layer. Reducing the time of the separation process reduces its efficiency. Reducing the thickness of the bulk body to a certain limit, as a rule, increases the efficiency of the separation process. A further decrease in the layer thickness below a certain value leads to a decrease in the efficiency of the process.

Consequently, in transport equipment, in order to increase its productivity, the transporting working body must be informed of an asymmetric law of oscillations with the greatest difference in the magnitude of the values of the maximum positive and negative acceleration.

In separation processes, the effect of vibrations on a free-flowing body is manifested in loosening and self-sorting of this body on the one hand, and in feeding, which ensures the continuity of the process, on the other. Sometimes the efficiency of the separation process is determined primarily by self-sorting. Examples of such processes are: cleaning grain from equal-size mineral impurities in stone separating machines; the process of sieve separation, in which there is little throughput, and the thickness of the granular body is many times greater than the size of the particles, while only the particles in the lower layer are sieved through the sieve, into which they fall due to self-sorting. If the concentration of the pass-through component in the initial mixture is high, as, for example, when cleaning grain from coarse impurities in a separator or when sieve separation of a grain mixture with a high concentration of a fine fraction, then self-sorting does not have a large effect on the results of the process as a whole and sieving becomes decisive.

According to the above, in separating machines, the parameters of the oscillation law of the working body must correspond to the type of process carried out in the machine. If necessary, the law of oscillation of the working body must ensure effective self-sorting of the grain mixture. The efficiency of self-sorting is in direct proportion to the duration of vibration exposure to the bulk body. In the implementation of the separation process, the efficiency of which is determined by the efficiency of the screening process, the law of oscillations of the working body must ensure the optimum speed of the particles of the bulk body relative to the screen surface for screening. The direction of asymmetry of the vibration law in combination with the inclination of the working surface to the horizontal and the communication of the surface of inclined vibrations opens up wide possibilities for varying the speed of vibration displacement.

It should be noted that the proposed method allows you to reverse the direction of the largest in absolute value of the force factor, excited by the vibration exciter. This means that the setting of the vibration exciter allows you to change to the opposite direction of transportation of the processed material along the vibrating working surface. This effect of adjusting the parameters of the laws of fluctuations of force factors can be used in drives of transport equipment, equipment for the implementation of separation processes, dosing and mixing of bulk materials.

The objective of the invention is to improve the equipment for the transportation and separation of grain mixtures by communicating to the working bodies of machines the movement according to the laws, the parameters of which correspond to the process carried out in the equipment.

The problem is solved by the proposed method of excitation of mechanical oscillations of force factors (force or moment) according to an asymmetric law by a centrifugal vibration exciter, consisting of four unbalances, the axes of rotation of which are located on a common base, having the same imbalances in pairs and have an initial position in which their centrifugal forces of inertia create maximum power factors, and rotating with the same angular velocities, which is ensured by a transmission that synchronizes and phase-matches the rotation of the unbalances with a gear ratio equal to the ratio of the angular velocity of rapidly rotating unbalances to the angular velocity of slowly rotating ones, according to the invention, to obtain a force factor with the greatest by an absolute value directed against the direction of the force factor created by rapidly rotating unbalances, change the initial position of slowly rotating unbalances by rotating them in any direction by an angle equal to th product, quotient of dividing 180 ° by the value of the gear ratio of the gear synchronizing and phase matching the rotation of the unbalances, by a number from the range of values from zero point two tenths to twice the value of the gear ratio minus zero point two tenths with a step equal to zero point four tenths at provided that the gear ratio is a fractional number, the integer part of which is an even number, and the fractional part is zero point four tenths.

The technical result is to vary the magnitude and direction of the transportation speed and to increase the technological efficiency of the separation processes of grain mixtures.

To communicate vibrations to the working bodies of machines with parameters corresponding to the process being carried out, we use a centrifugal vibration exciter with four unbalances.

является передаточным отношением передачи, синхронизирующей и согласовывающей по фазе вращение первой и второй пар дебалансов.Imbalances, that is, the product of the unbalanced mass m by its eccentricity r relative to the axis of rotation, of two unbalances of one pair must be equal to each other. These unbalances must have the same rotational speed ω. The imbalances of the second pair of unbalances must also be equal to each other and may differ in magnitude from the imbalances of the first pair of unbalances. The unbalances of the second pair should have the same rotational speed, but different from the rotational speed of the first pair of unbalances. Let's keep the previously accepted numbering of unbalances. Let us consider the first pair of unbalances to be unbalances rotating with frequency ω ₁ = ω, and the second pair - with frequency ω ₂ = nω, n is a fractional number of the form i + 0.4, where i is an even number. Obviously, n> 1, that is, the second pair of unbalances rotates at a higher frequency. The rotation of the unbalances must be appropriately synchronized and phase-matched. This can be achieved through either a gear (gear) transmission, or a toothed belt transmission, that is, a transmission that excludes slippage of the driving and driven links. Note that the relation

is the gear ratio of the transmission synchronizing and phase matching the rotation of the first and second pairs of unbalances.

Such a vibration exciter allows one to obtain various laws of oscillation of force factors (force or moment). These force factors, depending on the design (location) of the vibration exciter, are either transmitted directly to the working body of the machine, or to the output link of the actuator associated with the working body.

As noted above, the asymmetry of the law of fluctuations of force factors means that the greatest positive value of the force factor is not equal to the absolute value of its greatest negative value. For definiteness of further reasoning, we introduce the concept of the direction of asymmetry of the law of oscillations of the excited force factor. The asymmetry of the oscillation law is considered positive if the largest positive value of the force factor is greater than the absolute value of the largest negative value of the force factor. The asymmetry of the oscillation law is negative if the absolute value of the largest negative value of the force factor is greater than the largest positive value of the force factor. We will consider such an initial phasing of unbalances, in which the vibration exciter excites oscillations of the force factor according to an asymmetric law and the gear ratio of the gear synchronizing and phase matching the rotation of the unbalances is a fractional number of the form n = i + 0.4, where i is an even number. As noted above, with such a phasing of the unbalances, the forces of inertia of slowly and rapidly rotating unbalances in the initial position should create the maximum force factors. Obviously, in this initial position, the inertial forces slowly and rapidly rotating unbalances can create force factors of the same or opposite direction. For definiteness of further reasoning, we will assume that in the initial position the forces of inertia of slowly and rapidly rotating unbalances create the maximum force factors of the same direction. Let's take this direction as positive.

при одинаковых условиях начальной фазировки дебалансов и при одинаковых соотношениях максимального значения силового фактора, создаваемого силами инерции медленновращающихся дебалансов к максимальному значению силового фактора, создаваемого силами инерции быстровращающихся дебалансов. Выполнение последнего условия означает, что в уравнениях (8) и (10) коэффициенты а и b равны друг другу, то есть а=b. Поэтому в дальнейших рассуждениях зависимость возбуждаемого силового фактора будем обозначать в общем виде как ƒ(δ). Очевидно, что выводы, полученные при исследовании рассматриваемых зависимостей, характеризуют параметры законов колебаний, как силы, так и момента.It should be noted that, as noted above, such a vibration exciter containing four unbalances, depending on the conditions for phasing the unbalances, can excite either force fluctuations or torque fluctuations. In this case, the characteristics of the laws of vibrations in dimensionless expression coincide at the same values of the gear ratio

under the same conditions of the initial phasing of the unbalances and with the same ratios of the maximum value of the force factor created by the inertial forces of slowly rotating unbalances to the maximum value of the force factor created by the inertial forces of the rapidly rotating unbalances. The fulfillment of the last condition means that in equations (8) and (10) the coefficients a and b are equal to each other, that is, a = b. Therefore, in further considerations, the dependence of the excited force factor will be denoted in general form as ƒ (δ). Obviously, the conclusions obtained in the study of the dependences under consideration characterize the parameters of the laws of oscillations, both force and moment.

As noted above, the dependence of the force factor is asymmetric if, in the initial position, slowly and rapidly rotating unbalances create maximum force factors of the same direction and if the gear ratio of the transmission synchronizing and phase matching the rotation of the unbalances is a fractional number of the form n = i + 0.4 , where i is an even number. In this case, the dependence of the force factor in the general case is described by the equation ƒ (δ) = α cosδ + cos nδ, and the largest force factor in absolute value has a positive direction, which coincides with the direction of the force factors created by inertial forces of slowly and rapidly rotating unbalances in the initial position.

соотношение максимальных силовых факторов, создаваемых силами инерции медленно и быстровращающихся дебалансов.Let us estimate the influence of the initial phasing of slowly rotating unbalances on the direction of the maximum force factor in absolute value, excited by the vibration exciter. Obviously, to assess the effect of the initial phasing of slow-rotating unbalances, it is necessary to keep the settings of the vibration exciter unchanged, which affect the characteristics of the oscillation law. These parameters include: initial phasing of rapidly rotating unbalances; gear ratio

the ratio of the maximum force factors created by the inertial forces of slowly and rapidly rotating unbalances.

является дробным числом вида n=i+0,4, где i - четное число. В этом случае исходным начальным положением дебалансов является такое их положение, при котором силы инерции быстро и медленновращающихся дебалансов создают силовые факторы, максимальные по величине одинакового направления (фиг. 6) и (фиг. 7). Следовательно, неизменным начальным положением быстровращающихся дебалансов является положение, в котором их центробежные силы инерции создают максимальный по величине силовой фактор в положительном направлении.As agreed above, we will investigate the effect of the initial phasing of slowly rotating unbalances in a vibration exciter designed to excite asymmetrical oscillations of force factors, provided that the gear ratio

is a fractional number of the form n = i + 0.4, where i is an even number. In this case, the initial initial position of the unbalances is their position in which the forces of inertia of rapidly and slowly rotating unbalances create force factors that are maximum in magnitude of the same direction (Fig. 6) and (Fig. 7). Consequently, the constant initial position of rapidly rotating unbalances is the position in which their centrifugal forces of inertia create the maximum force factor in the positive direction.

Let us change the conditions for the initial phasing of the slowly rotating unbalances by rotating them from their initial initial position by some arbitrary angle γ. The figure (Fig. 8) shows the new initial position of the unbalances in the vibration exciter designed to excite force oscillations. The new initial position of the unbalances differs from the initial initial position in that the slowly rotating unbalances are rotated relative to the initial position by an arbitrary angle γ in the direction of their rotation.

Then the dependence of the excited force factor in dimensionless expression with a new initial position of the unbalances can be represented as

where γ is the angle of detuning of the slowly rotating unbalances from the initial position, in which their inertial forces create the maximum force factor.

Let us determine the values of the angle γ at which such a change in the initial position of the slowly rotating unbalances is accompanied by a change in the opposite direction of the largest in absolute value force factor, excited by the vibration exciter.

It should be noted that if the gear ratio n is a fractional number of the form n = i + 0.4, where i is an even number, then the kinematic cycle of the vibration exciter mechanism, that is, the time after which the unbalances return to their initial position, corresponds to five revolutions of slowly rotating unbalances. In this case, the number of revolutions of rapidly rotating unbalances is equal to five times the value of the gear ratio.

When determining the values of the angle γ, it should be borne in mind that the angle γ can take values in the range from 0 ° to 360 °, since the periodic function cosδ has a period of 360 °.

The direction of the largest force factor in absolute value will change to the opposite, that is, from a positive direction to a negative one, if, with a new initial phasing of unbalances, they can take a position in which the forces of inertia of rapidly and slowly rotating unbalances will simultaneously create maximum force factors in the negative direction.

If quickly and slowly rotating unbalances occupy a position in which their centrifugal forces of inertia simultaneously create maximum force factors in the negative direction, then the following system of equations has a solution

The solution to the first equation of the system is the following values of the angle of rotation of rapidly rotating unbalances from the initial position

where k = 0, 1, ..., 5n-1;

n is the gear ratio of the gear that synchronizes and phase-matches the rotation of the unbalances.

In this case, the slowly rotating unbalances will occupy positions corresponding to the following values of the angle δ of their rotation from the initial initial position, that is, the position in which their inertial forces create the maximum force factor of the positive direction

As noted above, the angle γ can take values in the range from 0 ° to 360 °, and the slowly rotating unbalances make five revolutions during the kinematic cycle of the vibration exciter mechanism. Therefore, the second equation of system (12) has the following roots:

and

Let us determine the angle γ for the case when δ + γ = 180 °. Equation (15) implies that

Substitute in equation (21) the value of the angle δ from equation (14) and after transformations we obtain

From equation (22) it follows that the angle γ is obtained as a result of multiplying two factors. The first factor is the quotient of dividing 180 ° by the value of the gear ratio n of the gear that synchronizes and phase-matches the rotation of the unbalances. This factor is a constant value, since it depends only on the value of the gear ratio n of the gear used in the vibration exciter to synchronize and match the unbalance rotation phase. The second factor, the expression in parentheses on the right side of equation (22), is variable due to the variability of the coefficient k. Coefficient k is included in formula (13) to determine the angles of rotation of rapidly rotating unbalances to positions in which their inertial forces create the maximum force factor in the negative direction. As noted above, the coefficient k can take values in the range from zero to 5n-1, since the number of revolutions of the rapidly rotating unbalances for the kinematic cycle of the vibration exciter mechanism is equal to five times the gear ratio n.

Let us determine the maximum and minimum values of the coefficient k, bearing in mind that the values of the angle γ of detuning of the slowly rotating unbalances from the initial initial position are in the interval 0 ° <γ <360 ° and that the maximum value of the coefficient k is 5n-1.

Obviously, in accordance with the conditions of the problem, the angle γ must, first, take positive values, and second, must be less than 360 °. Therefore, the condition must be met - the expression in parentheses of equation (22) must be greater than zero and less than twice the gear ratio, that is, the inequality must be satisfied

First, consider the fulfillment of the condition

Using the accepted designation of the gear ratio n = i + 0.4 of the gear synchronizing and phase matching the rotation of the vibration exciter unbalances, after the transformations, we rewrite inequality (24) in the form

In the general case, the right-hand side of the last inequality is a series of odd numbers. Since the integer part i of the fractional number n is an even number, the maximum value of the coefficient k is determined from the equation

Then

Let us express the maximum value of the coefficient k through the value of the gear ratio n of the gear that synchronizes and phase-matches the rotation of the unbalances. According to the accepted designation of the gear ratio, the integer part i of the fractional number n is equal to i = n-0.4. Let's substitute this value i in the formula (27). After transformations we get

Note that in the case under consideration (δ + γ = 180 °), the thus obtained maximum value of the coefficient k does not exceed its maximum allowable value equal to 5n-1. That is, in the case under consideration, which meets the condition δ + γ = 180 °, the coefficient k can take values less than 5n-1.

The second condition of inequality (23)

is performed for any values of the coefficient k. Therefore, the minimum value of the coefficient k is zero, that is, k _min = 0. It should be noted that in the case under consideration, the minimum value of the coefficient k does not depend on the value of the gear ratio n of the transmission, which synchronizes and phase-matches the rotation of the vibration exciter unbalances.

To simplify further reasoning, we introduce the notation. We denote the variable factor of the right-hand side of equation (22)

To determine the minimum and maximum values of the variable factor c, we substitute k _max and k _min into equation (30), respectively. We get

и

and

As noted above, the coefficient k is a series of natural numbers, including zero, and the maximum value of the coefficient k is 5n-1. Therefore, determining the minimum and maximum values of the coefficient k for a given value of the gear ratio n, we determine how many and what values the coefficient k has, as well as how many and what values the variable factor c _{1 has} in the case under consideration. For example, in this case, if the gear ratio n of the gear synchronizing and phase matching the rotation of the unbalances is n = 2.4, then k _max = k _min = 0 and c _1max = c _1min = 1.4. If the gear ratio is n = 4.4, then k _max = 1. Therefore, the coefficient k takes the following values: 0 and 1. The variable factor with ₁ takes the following values: 3.4 and 1.4.

Similarly, we determine the values of the angle y of detuning slowly rotating unbalances from the initial initial position for the remaining values of the roots of the second equation of the system of equations (12).

We will not dwell on a detailed description of this solution. Let us note only certain points necessary for clarification of the actions performed when solving the problem.

Let us determine what values the angle γ takes on the condition that the root of the second equation of system (12) is represented by equation (16). Equation (16) implies that

We substitute the value of the angle δ from equation (14) into equation (33) and after transformations we obtain

Two conditions must be met, represented by the following inequality

Consider the first condition

After the appropriate substitution and transformations, we obtain

The maximum value of the coefficient k is determined from the condition

Then

Let us express the maximum value of the coefficient k through the gear ratio n. We get

Consider the fulfillment of the second condition of inequality (35), namely the condition

After substitution n = i + 0.4 and transformations, we get

The right side of inequality (42) is a series of odd numbers. The integer part i of the fractional number n is an even number. Therefore, the minimum value of the coefficient k is determined from the condition

After transformations we get

We denote the variable factor of equation (34)

The minimum and maximum values of the variable factor are respectively equal

and

Note that in the considered case, which meets the condition δ + γ = 540 °, with the gear ratio n of the gear synchronizing and phase matching the rotation of the unbalances equal to n = 2.4, the maximum and minimum values of the coefficient k are respectively equal to k _max = 3 , k _min = 1, and the maximum and minimum values of the variable factor c _{2 are} respectively equal to c _2max = 4.2, c _2min = 0.2. Therefore, in this case, the coefficient k takes the following values: 3; 2 and 1. In this case, the variable factor with ₂ takes the following values: 0.2; 2.2 and 4.2. If the gear ratio n = 4.4, then the minimum and maximum values of the coefficient k are respectively equal to k _min = 2 and k _max = 6. Therefore, in this case, the coefficient k takes the following values: 2; 3; 4; five; and 6. In this case, the variable factor with ₂ takes the following values: 0.2; 2.2; 4.2; 6.2; and 8.2.

Let us determine the values of the angle γ for the case when the root of the second equation of system (12) is represented by equation (17). Equation (17) implies that

We substitute the value of the angle δ from equation (14) into equation (48) and after transformations we obtain

Two conditions must be met, represented by the following inequality

Consider the fulfillment of the first condition, namely, the condition

After the appropriate substitution and transformations, we obtain

The maximum value of the coefficient k is determined from the condition

Equation (53) implies

Let us determine at what values of the coefficient k the second condition of inequality (50) is satisfied, namely, the condition

After the appropriate substitution and transformations, we obtain

The right side of the last inequality is an odd number. The product 3i is an even number because the integer part i of the fractional number n is an even number. Consequently, the minimum value of the coefficient k at which inequality (56) is satisfied is determined from the condition

From equation (57) we obtain

The variable factor of equation (49) is denoted

In the case under consideration, the minimum and maximum values of the variable factor c ₃ are

and

Let us determine, as an example, how many and what values the coefficient k and the variable factor c _{3 take} in the case under consideration for two different values of the gear ratio n of the transmission synchronizing and phase matching the rotation of the unbalances. For n = 2.4, the minimum and maximum values of the coefficient k and variable factor c _{3 are} respectively equal: k _min = 4, k _max = 5 and c _3min = 1, c _3max = 3 Therefore, in this case, the coefficient k takes the following values: 4 and 5, and the variable factor with ₃ is the following values 1 and 3. For n = 4.4, the minimum and maximum values of the coefficient k are, respectively, k _min = 7 and k _max = 10. Therefore, in this case, the coefficient k takes the following values: 7; 8; 9 and 10. In this case, the variable factor with ₃ takes the following values: 7; five; 3 and 1.

In the case when the root of the second equation of the system of equations (12) can be determined from equation (18), the angle γ is determined by the formula

Two conditions must be met, which can be represented by the following inequality

Let us determine at what values of the coefficient k the condition

After the appropriate substitution and transformations, we obtain

Therefore, the maximum value of the coefficient k is determined from the condition

From equation (66) we have

Let us determine at what values of the coefficient k the condition

After transformations and corresponding substitution, we have

The minimum value of the coefficient k is determined from the condition

From equation (70) we have

We denote the variable factor of equation (62)

To determine the minimum and maximum values of the variable factor with _{4, we} substitute into equation (72) the values of k _max and k _min, respectively, from equations (67) and (71)

and

Let us determine the value of the angle γ for the fifth value of the root of the second equation of the system of equations (12). Equation (19) implies that

After substituting equation (14) into equation (75) and transformations, we obtain

Since 0 ° <γ <360 °, then the inequality must be satisfied

Let us determine what values the coefficient k can take under the condition

We write inequality (78) in the form

The maximum value of the coefficient k is determined from the condition

Then

Let us determine what values the coefficient k can take when the second condition of inequality (77) is satisfied, namely, the condition

After transformations we get

The minimum value of the coefficient k is determined from the condition

Then

We denote the variable factor of equation (76)

To determine the minimum and maximum values of the variable factor with _{5, we} substitute in equation (86) the values of k _max and k _min, respectively, from equations (81) and (85)

and

Let us determine the value of the angle γ for the sixth value of the root of the second equation of the system of equations (12). Equation (20) implies that

After substituting equation (14) into equation (89) and transformations, we obtain

Since 0 ° <γ <360 °, then the inequality must be satisfied

Let us determine what values the coefficient k can take under the condition

We rewrite inequality (92) as

The maximum value of the coefficient k can be determined from the condition

Then

Note that the maximum value of the coefficient k calculated by the formula (95) exceeds the maximum value of the coefficient, the value of which is determined from the condition of the duration of the kinematic cycle of the vibration exciter mechanism. Obviously, it is advisable to take the maximum value of the coefficient k _max = 5n-1, determined from the condition of the duration of the kinematic cycle of the vibration exciter mechanism. The use of the maximum value of the coefficient k, determined by the formula (95), leads to the determination of the overlapping values of the angle γ. This is due to the fact that the dependence of the force factor excited by the vibration exciter is a periodic function with an unlimited number of periods.

Let us determine what values the coefficient k can take when the second condition of inequality (91) is satisfied, namely the condition

We write inequality (96) in the form

The minimum value of the coefficient k is determined from the condition

From equation (98) we have

We denote the variable factor of equation (90)

To determine the minimum and maximum values of the variable factor with _{6, we} substitute into equation (100) the values k _max = 5n-1 and k _min from equation (99)

and

Summarizing the results obtained, considering how many and what values the coefficient k and the variable factor c can take in the formulas for determining the angle γ in each of the considered cases, we can draw the following conclusion. The system of equations (12) has a solution if the angle γ is defined, firstly, as the product of two factors: the first factor is equal to the quotient of dividing 180 ° by the value of the gear ratio n of the transmission synchronizing and phase matching the rotation of the unbalances; the second factor sequentially takes values equal to numbers from the range of values from zero point two tenths to twice the value of the gear ratio minus zero point two tenths with a step equal to zero point four tenths, and secondly, provided that the gear ratio n is a fractional number, an integer the part of which is an even number, and the fractional part is zero point four tenths.

The presented conclusions correspond to the case when, in order to obtain the force factor with the highest absolute value directed against the direction of the force factor created by rapidly rotating unbalances, the initial position of the slowly rotating unbalances is changed by rotating them by an angle γ in the direction of their rotation.

Similar conclusions were obtained for the case when the initial position of the slow-rotating unbalances is changed by turning them in the direction opposite to the direction of rotation of the unbalances, that is, when the slow-rotating unbalances are rotated by an angle - γ.

In this case, the dependence of the force factor in dimensionless expression has the form

With such a change in the initial position of the slowly rotating unbalances, the vibration exciter creates a force factor with the highest absolute value, directed against the direction of the maximum force factor created by the rapidly rotating unbalances, provided that the system of equations has a solution

We will not dwell on the solution of the system of equations (104); its solution is similar to the solution of the system of equations (12) considered in detail above. Let us note some common and distinctive features in determining the positive and negative values of the angle γ.

Note that the first equation of the system of equations (104) coincides with the first equation of the system (12). Therefore, the roots of the first equation of system (104) can be determined by formula (14). The second equation of system (104) has the following roots:

and

Let us consider the peculiarity of determining negative values of the angle γ using the example of the first root of the second equation of the system of equations (104).

Equation (105) implies that

After substituting the expression for the angle δ from equation (14) into the last equation and transformations, we obtain

, либо к переменному сомножителю с₁=n-1-2k. Очевидно, что аналогичные формулы могут быть получены при определении отрицательных значений угла γ для пяти других корней второго уравнения системы (104). Для определенности дальнейших рассуждений будем считать, что в уравнениях для определения отрицательных значений угла γ знак минус относится к переменному сомножителю.Equation (112) for determining negative values of the angle γ differs from equation (22) for determining positive values of the angle γ only in sign. The minus sign in equation (112) can be assigned either to a constant factor

, or to a variable factor with ₁ = n-1-2k. Obviously, similar formulas can be obtained when determining negative values of the angle γ for five other roots of the second equation of system (104). For definiteness of further reasoning, we will assume that in the equations for determining negative values of the angle γ, the minus sign refers to the variable factor.

Let us note some common and distinctive features in determining the positive and negative values of the angle γ. In both cases, the angles γ are equal to the product of two factors. The first factor in both cases has the same value, equal to the quotient of dividing 180 ° by the value of the gear ratio n of the gear that synchronizes and phase-matches the rotation of the unbalances. The difference in determining the positive and negative values of the angle γ is as follows. In the first case, for γ> 0 °, the second factor sequentially takes values equal to numbers from the range of values from zero point two tenths to twice the gear ratio n minus zero point two tenths, with a step of zero point four tenths. In the second case, for γ <0 °, the second factor sequentially takes negative values equal in absolute value to numbers from the range of values from zero point two tenths to twice the value of the gear ratio n minus zero point two tenths, with a step of zero point four tenths ... That is, the difference lies only in the sign of the second factor in the formula for determining the values of the angle γ. The number of positive values of the angle γ is equal to the number of negative values of the angle and is equal to five times the value of the gear ratio n of the transmission, which synchronizes and phase-matches the rotation of the unbalances. In this case, each positive value of the angle γ corresponds to a negative value of the angle corresponding to the condition: the sum of the absolute values of these angles is 360 °. Let us prove this statement.

We represent the formula for determining the positive values of the angle γ in the form

where c ₊ = 0.2; 0.6; ...; 2n-0.2 is a factor that sequentially takes values equal to numbers from a series of numbers from zero point two tenths to twice the gear ratio n minus zero point two tenths, in increments of zero point four tenths.

Then the formula for determining negative values of the angle γ can be represented as

where c _- = -0.2; -0.6; - (2n-0.2) is a factor that sequentially takes values equal to negative values of numbers from a range of values from zero point two tenths to twice the value of the gear ratio n minus zero point two tenths, with a step of zero point four tenths.

We represent positive values of the angle γ as a numerical series in which the members of the series are arranged in ascending order of their values, and negative values of the angle γ will be represented as a numerical series in which the members of the series are arranged in descending order of their absolute values. It should be noted that when determining the numerical values of the members of the first numerical series, starting with the first member of the series, the minimum in value, and ending with the last, maximum in value, the factor c ₊ sequentially takes values equal to numbers from 0.2 to 2n-0.2 ... Moreover, each subsequent value of the factor c ₊ differs from the previous one by zero point four tenths. When determining the numerical values of the members of the second numerical series, starting with the first, maximum in absolute value, member of the series, and ending with the last, minimum in absolute value, the factor c _- sequentially takes values equal in absolute value to numbers from 2n-0.2 to 0 , 2. Moreover, each subsequent value of the factor c _- differs from the previous one by zero point four tenths. Hence, we can conclude: the factors c ₊ and c _- for the same-named members of the first and second numerical series are interconnected by the dependence

The value of some arbitrary member of the first numerical series is determined by the formula

Then the absolute value of the corresponding member of the second numerical series should be determined by the formula

As can be seen from equations (116) and (117), the sum of their right-hand sides is 360 °, that is, γ _{j +} + | γ _j- | = 360 °, which was required to prove.

Note that the following condition can be easily proved using well-known formulas.

The cosine of the sum of two angles is equal to the cosine of the difference between two angles, if the first term in the sum of the angles is equal to the one that is decreasing in the difference of angles, and the second term in the sum of angles and subtracted in the difference of angles are the values of the angles that complement each other up to 360 °, that is

if γ ₁ = 360 ° - γ or, which is the same, if γ = 360 ° - γ ₁ .

Thus, to confirm the proposed method for determining the values of the angle γ, it is sufficient to investigate the dependence of the force factor either at positive values of the angle γ, or at negative ones.

To confirm the results of the theoretical determination of the values of the angle γ, the dependences ƒ (δ) = cos nδ + cos (δ + γ) and ƒ (δ) = cos nδ + cos (δ-γ) of the force factors were investigated at the values of the gear ratio n of the gear synchronizing and phase matching the rotation of the unbalances equal to 2.4; 4.4; 6.4 and 8.4. When studying the dependences at the selected value of the gear ratio n, the values of the angle γ were calculated. For the calculated values of the angle γ, the graphs of dependences of force factors were built and these dependences were investigated for extrema.

Figures (Fig. 9), (Fig. 10), (Fig. 11), (Fig. 12), (Fig. 13), (Fig. 14) and (Fig. 15) show the dependence of the force factor as an example for the case: the gear ratio of the gear synchronizing and phase matching the unbalance rotation is equal to n = 2.4; the ratio of the maximum force factors created by the inertial forces of slowly and rapidly rotating unbalances is equal to unity, that is, for the case when the coefficient a = 1. In the figure (Fig. 9), the dependence corresponds to the initial position of the unbalances, in which the forces of inertia of slowly and rapidly rotating unbalances create the maximum force factors in the positive direction. It should be noted that this initial position of the unbalances is shown in figures (Fig. 6) and (Fig. 7) in vibration exciters: to excite force oscillations (Fig. 6); to excite the oscillations of the moment (Fig. 7). As can be seen from the figure (Fig. 9) the maximum positive value of the force factor is greater than the maximum absolute value of the force factor in the negative direction. In the case under consideration, 2.0> | -1.97 |. Figures (Fig. 10), (Fig. 11), (Fig. 12), (Fig. 13), (Fig. 14) and (Fig. 15) show the dependences of the force factors for the initial positions of slowly rotating unbalances at positive values of the angle γ, determined by the method proposed above. In the case under consideration (n = 2.4), the angle γ takes the following values: 15 °; 45 °; 75 °; 105 °; 135 °; 165 °; 195 °; 225 °; 255 °; 285 °; 315 ° and 345 °. It should be noted that such an initial position of the unbalances is shown in the figure (Fig. 8) for some arbitrary positive value of the angle γ. As can be seen from the drawings (Fig. 10), (Fig. 11), (Fig. 12), (Fig. 13), (Fig. 14), (Fig. 15), (Fig. 16), (Fig. 17 ), (Fig. 18), (Fig. 19), (Fig. 20) and (Fig. 21) dependencies have the same direction of the maximum force factor in absolute value. At the same time, the maximum positive value of the force factor is less than the maximum in absolute value of the force factor in the negative direction (| -2.0 |> 1.966). It should be noted that at the initial positions of the slowly rotating unbalances corresponding to the following values of the angle γ: γ = 15 °; 45 °; 75 °; 105 °; 135 ° 165 °; 195 °; 225 °; 255 °; 285 °; 315 ° and 345 °, the direction of the maximum absolute value of the force factor excited by the vibration exciter is opposite to the direction of the maximum force factor created by the inertial forces of rapidly rotating unbalances in the initial position.

The results of determining the extrema of the dependences of the force factor at negative values of the angle γ confirmed the earlier conclusion. With a gear ratio equal to n = 2.4, the angle γ has the following negative values: -15 °; -45 °; -75 °; -105 °; -135 °; -165 °; -195 °; -225 °; -255 °; -285 °; -315 ° and -345 °. When studying these dependencies, it was found that the dependence ƒ (δ) = cos2.4δ + cos (δ + 15 °) coincides with the dependence ƒ (δ) = cos2.4δ + cos (δ-345 °), since cos (δ + 15 °) = cos (δ-345 °). The dependence ƒ (δ) = cos 2.4δ + cos (δ + 45 °) coincides with the dependence ƒ (δ) = cos2.4δ + cos (δ-315 °), since cos (δ + 45 °) = cos ( δ-315 °). For the same reason, the dependencies are the same:

Thus, the above reasoning allows us to draw the following conclusion.

In a centrifugal vibration exciter containing four unbalances rotating around parallel axes located on a common base and having the same angular velocities and unbalances in pairs, occupying the initial position in which their centrifugal inertial forces create the maximum force factors, which is provided by a transmission that synchronizes and phase-matching the rotation of unbalances with a gear ratio equal to the ratio of the angular velocity of rapidly rotating unbalances to the angular velocity of slowly rotating ones, to obtain the force factor with the greatest absolute value directed against the direction of the force factor created by the rapidly rotating unbalances, change the initial position of the slowly rotating unbalances by turning them in any direction by an angle equal to the product of the quotient of dividing 180 ° by the value of the gear ratio of the transmission synchronizing and phase matching the rotation of the unbalances, by a number from the interval and from zero point two tenths to twice the value of the gear ratio minus zero point two tenths in increments of zero point four tenths, provided that the gear ratio is a fractional number, the integer part of which is an even number, and the fractional part is zero point four tenths.

The proposed method of excitation of mechanical vibrations of power factors with an adjustable direction of the maximum in absolute value of the power factor, excited by a vibration exciter, can be used to improve the transport and technological equipment of grain processing enterprises.

In the case of using the proposed method in transport equipment, the device operates as follows.

The axes of rotation of the unbalances are located on a common base (Fig. 16), rigidly connected to the working surface of the transporting device. The axes of rotation of the unbalances of the same name, that is, unbalances having the same unbalances and rotating with the same angular velocities, are located symmetrically relative to the perpendicular to the straight line connecting the axes of rotation of these unbalances. In this case, the axes of rotation of the first pair of unbalances and the axes of rotation of the second pair of unbalances are located symmetrically relative to one straight line. Note that with such an arrangement of the axes of rotation of the unbalances, the straight lines connecting the axes of rotation of the same unbalances must be parallel to each other. On the basis of (Fig. 16), the "+" sign marks the initial position of the unbalances, at which the forces of inertia of rapidly and slowly rotating unbalances create the maximum force factors (forces) of one (positive) direction. In this case, the direction of the maximum force factor, excited by the vibration exciter, coincides with the direction of the maximum force factor created by the rapidly rotating unbalances in the initial position. In the figure (Fig. 22) for the case when the gear ratio n of the gear synchronizing and phase matching the rotation of the unbalances is equal to n = 2.4 by the characters 01, 02, 03, 04, 05, 06, 07, 08, 09, 10 11 and 12 show twelve different initial positions of slowly rotating unbalances, at which the maximum force factor (force) excited by the vibration exciter has a direction opposite to the direction of the force factor created by the inertial forces of rapidly rotating unbalances in the initial position. In the figure (Fig. 22), slowly rotating unbalances are shown in one of twelve possible initial positions, in which the direction of the maximum in absolute value of the force factor excited by the vibration exciter is opposite to the direction of the maximum force factor created by the inertial forces of the rapidly rotating unbalances in the initial position. The dotted line shows the initial position of the slowly rotating unbalances when their inertial forces create the maximum force factor, and the maximum force factor excited by the vibration exciter coincides in direction with the direction of the maximum force factor created by the inertial forces of the rapidly rotating unbalances in the initial position.

It should be noted that with the design of the drive using the proposed method for regulating the parameters of oscillations of force factors, it is sufficient to use one of the possible initial positions of slowly rotating unbalances, which allow changing the maximum force factor excited by the vibration exciter to the opposite direction. This position should be the position that is the simplest in design in this particular equipment.

When the unbalances rotate, their centrifugal forces of inertia create a resultant force that oscillates rectilinearly according to an asymmetric law. Under the action of such a resultant force, the working surface performs rectilinear oscillations according to an asymmetric law, that is, the largest positive value of the surface acceleration is not equal to the modulus of the largest negative acceleration value.

The grain mixture enters the working surface and, under the influence of vibrations, is transported along it. The transport speed determines the performance of the transport equipment. The direction of the highest in absolute value acceleration of the working surface in combination with its inclination to the horizontal and the communication of the surface of inclined vibrations opens up wide possibilities for varying the transport speed.

In the case of application of the proposed method for regulating the direction of asymmetry of rectilinear oscillations of force in technological equipment for carrying out separation processes, the device operates as follows.

Let us consider the operation of the device by the example of cleaning a grain mixture from large impurities.

The initial grain mixture is fed to the sieve surface in a continuous flow, making rectilinear vibrations. Surface vibrations provide transportation of the grain mixture and its self-sorting. In the process of self-sorting, large impurities float to the upper layer of the grain flow. When moving, the particles of the grain mixture pass over the holes of the sieve surface and, when favorable conditions occur, are sieved. Since when cleaning grain from large impurities, the initial grain mixture consists mainly of passing (grain) particles, self-sorting does not have a large effect on the results of the process as a whole and sieving is of decisive importance. The proposed method of changing the direction of the maximum in absolute value of the force to the opposite direction, together with the use of the inclination of the working surface to the horizontal and the inclination of the direction of oscillations, create conditions for communicating the grain mixture to the speed relative to the working surface, which ensures the most efficient flow of the sifting process, that is, it allows the working body to communicate oscillations with parameters corresponding to the most efficient sieving process.

In a similar way, conditions can be created for the most effective implementation of the separation process, in which the self-sorting process is of decisive importance. Thus, the use of the proposed method for regulating the direction of asymmetry of the oscillation law makes it possible to increase the efficiency of screen separation.

In addition, the implementation of the proposed method of excitation of mechanical oscillations of force factors with adjustable parameters opens up the prospect of creating a unified drive for transport and technological equipment of grain processing enterprises.

List of references

1. Patentschrift No. 955 756 (DFR), K1. 81 e, Gr. 53, Intenat. K1. At 65 g, 01/10/1957.

2. RU 2528271 C2 30.10.2012.

3. RU 2528550 C2 21.12.2012.

Claims (1)

The method of excitation of mechanical vibrations of force factors with adjustable parameters by a centrifugal vibration exciter, exciting vibrations according to an asymmetric law, consisting of four unbalances, the axes of rotation of which are located on a common base, having the same imbalances in pairs, and have an initial position in which their centrifugal inertia forces create maximum force factors, and rotating with the same magnitude of angular velocities, which is ensured by a transmission that synchronizes and phase-matches the rotation of unbalances with a gear ratio n equal to the ratio of the angular velocity of rapidly rotating unbalances to the angular velocity of slowly rotating ones, characterized in that to obtain a force factor with the greatest an absolute value directed against the direction of the force factor created by rapidly rotating unbalances, change the initial position of slowly rotating unbalances by rotating them in any direction by an angle equal to maintaining the quotient from dividing 180 ° by the value of the gear ratio n of the gear synchronizing and phase matching the rotation of the unbalances, by a number from the range of values from 0.2 to 2n-0.2 with a step equal to 0.4, provided that the gear ratio n is a fractional number, the integer part of which is an even number, and the fractional part is zero point four.

Images