Having analyzed traditional methods for determining the coordinates of the center of gravity of machines, we developed a three-coordinate method using the simplest and most affordable means of hanging products with a crane beam. The method differs from analogues in the minimum number of weighings when there are no force-measuring means as a component of the measuring circuit. We introduce a mathematical model, which is the core of the method, and a computer model which minimizes the complexity of mathematical processing of measurement results

На основании результатов анализа традиционных методов определения координат центра тяжести машин разработан трехкоординатный метод с использованием наиболее простых и доступных средств подвешивания изделий кран-балкой. Метод отличается от аналогов минимальным числом взвешиваний при отсутствии в составе измерительной схемы силоизмерительных средств. Представлена математическая модель, лежащая в основе метода, и компьютерная модель, позволяющая минимизировать трудоемкость математической обработки результатов измерений

It is hard to overestimate the role of a precise and convenient method for determining the position of the center of gravity of manufactured products. The position of the center of gravity of a machine impacts such qualitative characteristics as traveling stability, buoyancy, distribution of load among supporting structures, smooth travel, etc. [

The simplest and most common (applied, among others, by JSC lEMZ “Kupol”) experimental method for determining the center of gravity of a machine is as follows. The tested machine (Pos. 1 in Fig. 1) is hung up using special brackets (Pos. 2) and slings (Pos. 3) attached to the cross-beam (Pos. 4). The cross-beam is lifted up using the crane beam. The center of gravity position in the uplifted position impacts sling load distribution. The coordinates of the center of gravity of a machine xc, yc are determined based on dynamometer (Pos. 5) readings using the equations of equilibrium for the hung-up machine:

Ti - sling tension load i.

This method has certain disadvantages, the most significant of which is impossibility to determine the elevation of the center of gravity zc.

An alternative method for determining the center of gravity is specified in [

The first weighing is performed with the body tilted in the longitudinal plane at angle a (Fig. 2, a). The tilt is ensured through lifting of the machine front part using the crane beam. The weighing results allow to determine the coordinate of the center of gravity ac by the formula

For the second weighing, the machine is tilted β to the opposite side in the same plane, through lifting the machine rear part (Fig. 2, b). The second coordinate of the center of gravity bc is determined by the formula

Points in plane Ω correspond to this coordinate.

The first two weighings limit the search region for the center of gravity to straight line h in the intersection of planes Θ and Ω. The exact position of the center of gravity on straight line h is determined by coordinate Xc, calculated by the formula

depending on the results of third weighing with the machine being in the horizontal position (Fig. 2, c). To determine the product actual mass m, one more weighing is required.

The standard method has an obvious advantage over the method applied at the enterprise due to the possibility of determining the elevation of the center of gravity, however, it requires platform weighing scale, increased number of weighings and it is more time consuming.

Among existing engineering solutions for determining the products center of gravity there is no method that would be simple and universal enough, as well as provide comprehensive information on the position of the center of gravity without increasing the amount of production equipment required for obtaining the same. Considering the above, the objective of this article is to develop a method for determining the spatial position of the center of gravity through hanging up using simple and widespread process means and subject to minimizing the use of special force-measuring instruments and the number of weighing operations.

For completing the experimental part of the process, we will forgo using special complex rigging in favor of load carrying one available in the shops: load cross-beam, slings and either frame crane or tower crane will be used. In this case, the objective can be achieved through estimating analytical relationships between the positions of a product hung up on the load cross-beam in the equilibrium condition and three coordinates of its center of gravity. The relationships can be expressed with the equations of equilibrium of the measuring system elements and analytic geometry equations, and their quantity and composition in a mathematical model can be chosen in such a way as to exclude force parameters from the list of independent variables (subject to experimental determination). This will allow to exclude the necessity of using force-measuring instruments as part of the measuring circuit.

Depending on the number of simultaneously processed coordinates, the considered problem may either be spatial or plane. The practical interest is the solution of the most common spatial problem. However, using the proposed method, it would be efficient to perform a preliminary abstract check of a principal possibility to determine the most problematic elevation coordinate by the example of solving the plane problem simple in mathematical terms.

Steady equilibrium condition of substatic system “cross-beam - slings - machine” depends on the coordinates of the center of gravity of the machine and the cross-beam. Two unknown coordinates of the machine center of mass can be determined similarly with the considered standard method, through hanging up the machine at two different angles. Hanging at different angles can be done through using pairs of slings of different length, while interchanging the pairs.

A combination of system “cross-beam - slings - machine” positions corresponds to every position of the center of gravity before and after interchanging the slings position. In order to provide analytical representation of this correspondence, let us refer to the system elements loading diagram for two cases shown in Fig. 3. Here, ADG - cross-beam hinge-mounted relative to the hanger with a single degree of freedom - rotation around hinge D. The position of the cross-beam is defined by angle γTi, where i ∈{ ,1 2} - sequence number of hanging operation. The cross-beam is characterized by the following known parameters: mass mT, dimensions HT and lT, position coordinates of its center of mass ZCT. AO and GK - slings with lengths l1 and l2 , respectively. Sling tension loads Tyi and T2i are deflected from the vertical by angles α1i and α2i, respectively.

The tested machine is conventionally shown as rectangle MNFE. Points O and K - slings fastening to the machine body (brackets). Point С - the machine center of gravity with unknown coordinates xc, zc relative to left bracket O in the machine coordinate system. Polar coordinates of the machine center of gravity - polar distance ρ and its tilt angle φ. The machine orientation in steady position i is defined by its angle of tilt with the horizontal γi. Other known machine parameters: mass n, dimensions LM and H, distance between brackets L, coordinate of the left bracket relative to the machine edge LO.

In the figure plane, we shall accept Cartesian coordinates xDz. We shall assume slings connections with the machine and the crossbeam to be perfect frictionless hinges, ignoring slings elongation under tension and slings mass.

Let us relate the system positions at two hanging operations with Cartesian coordinates of the machine center of gravity using the equations of equilibrium [

where AD - length of cross-beam arm, AD =

δ- angle at tops A and G of the crossbeam, ;

γ1 and γ2 - angles of machine tilt relative to the horizontal in the first case and second case, respectively; upper sign «+» is applicable to γ1, lower «-» to γ2.

Joint solution of two equations (1), compiled for each of two cases subject to known parameters of the system position (YТ1, YТ2, Y1, Y2, α11, α22), allows to determine polar coordinates of the machine center of gravity ρ and φ. Conversion to Cartesian coordinates of the center of gravity can be done using the known method [

Parameters γТ1, γТ2, γ1, γ2, α11, α22 are predetermined based on mathematical models describing each of two equilibrium positions of the system. The models contain the equations of equilibrium and equations expressing geometrical constraints of the system elements. Two force equations and one moment equation of cross-beam equilibrium are as follows

where tension force of hauling cable is defined by the formula

T = (m + mT) g. (6)

Geometrical equations express closedness of substatic tetragon AGKO:

In projections on axis z and x we will obtain two more equations

Thus, five equations are obtained for each case i with six variables: T1i,T2i, α1i, α2i, γTi, γi.. One of these variables can be considered independent and subject to measurement. The remaining five variables are defined depending on the same and using five obtained equations.

If geometrical variable, for example machine tilt angle Y i, is chosen as an independent variable, there will be no need to define force variables and, consequently, use forcemeasuring instruments. It is quite simple to define the tilt angle experimentally, for example, by the difference in elevation of two points of the machine: E and F above the floor level by the formula

Thus, we have ascertained the principal possibility to determine the center of gravity elevation coordinate through hanging up and the absence of the need to use any forcemeasuring instruments for this purpose.

As the second step, let us solve the spatial problem and develop an algorithm for determining the position of the center of gravity.

The spatial problem solution is very similar to the plane problem solution. The main differences are in the increased number of parameters describing equilibrium conditions of the measuring system elements, which are defined by a large number of jointly solved equations.

When solving the spatial problem, it is convenient to use matrix formulas at spatial turns and shifts [

Calculation patterns of the system in space for two weighings are shown in Fig. 4. The position of the cross-beam ABDEF in case i is set by the angles of its rotation around own coordinate axes γTix, γTiy and γTiz, nA - vector of normal to the plane of figure BDEF. Tjik - projections of sling tension force j in case i to coordinate axis k.

If the matrix of spatial coordinates of the cross-beam nodal points prior to its rotation around own axes passing through hinge А is as follows

then, in steady equilibrium condition, the coordinates of nodal points depend on the angles of crossbeam orientation γTiy and γTiz in accordance with the known formula

The coordinates of sling ends are connected with the coordinates of cross-beam nodal points with the equation

where Tij - sling tension loads, Tij =

BO, DG, FM, EK - length of slings elongated under tension.

According to Hooke’s law, sling length j in elongated condition - lj + JljTji,, where J - lengthwise sling elasticity [

The coordinates of nodal points provided in equations (10) and (11) are used in mathematical models of system position in two cases.

The mathematical models represent a complex of equilibrium equations and geometrical equations. Six cross-beam equilibrium equations for case i are as follows

where T - tension force of hauling cable, defined by the formula (6);

m B ∈ (B, E, F, D), - dependencies of the nodal points coordinates on the cross-beam orientation angles, calculated by the formula (10).

Geometrical equations express the condition of closedness of substatic tetragons BOKE and BOMF at different machine spatial orientation γiy и γiz:

In the projections on the coordinate axes considering (10) and (11), we will additionally get nine equations:

Subject to known machine orientation angles, the system of fifteen equations (12) - (26) solved relative to 15 variables - T1ix , T1iy , T1iz, T2ix , T2iy , T2iz, T3ix , T3iy , T3iz, T4ix , T4iy , T4iz, γTix , γTiy , γTiz - allows to completely define the parameters of system position in this case i.

The angles of machine spatial orientation γix , γiy and γiz in case i are calculated based on matrix transformation of the coordinates of three points V, Q, R at machine rotation (see Fig. 4):

If based on formula (21) we express the differences between elevation coordinates of points V, Q, R pairwise and equate them with the differences between measured elevation of these points above the floor level, we will obtain a system of three equations for defining angles

The parameters of system position in two cases are required for defining the coordinates of the machine center of gravity based on moment equations of equilibrium

where functional dependencies of the machine center of gravity coordinates in system xyz on the coordinates of the center of gravity in own coordinate system XC, YC, ZC:

functional dependencies of the cross-beam nodal points coordinates on its orientation angles are expressed based on the formula (10).

Through solving equations (29) relative to XC, YC, ZC, we define the unknown position of the machine center of gravity.

Thus, subject to known parameters of measur - m, mT , ZcT , HT ,aT , bT , L, LM , LO, B, l1, l2, l3, l4, J - the algorithm of defining the machine center of gravity in space includes the following steps:

The program was written in MathCAD to reduce labour intensity connected with mathematical processing of the measurement results. The advantages of using MathCAD for solving this problem are based on the built-in tools for solving non-linear equation systems.

The developed program allows automatic calculation of the coordinates of the machine center of gravity depending on the parameters of the measuring system and depending on the measured elevations of the machine points V, Q, R above the floor level for two cases of hanging. The program outputs numeric values of the coordinates and shows the positions of measuring system with the elements’ centers of gravity in three projections for each case, as well as the machine center of gravity in own coordinate system in three projections. The examples of the program operation results are shown in Fig. 5.

The developed method of determining the coordinates of the center of gravity of a machine does not require use of force-measuring instruments as part of the measuring circuit, is targeted at using simple hanging up facilities available in the shop, allows to determine all three coordinates of the center of gravity and is a good alternative for the method used at the enterprise.

The program written based on the developed algorithm allows to reduce labour intensity connected with mathematical processing of the measurement results.

This article provides a consideration of a principal possibility to determine the center of gravity using the proposed method, based on mathematical processing. Within the framework of further works, the accuracy of the method will be assessed, the effect of errors of the applied means on the error of the center of gravity determination will be studied, the results of pilot testing carried out at the JSC IEMZ “Kupol” production facilities will be provided.

The authors declare that there are no conflicts of interest present.