Published: 07 October 2016

Dynamics rammers with two pairs of shock generators

L. A. Igumnov1
V. S. Metrikin2
I. V. Nikiforova3
1, 2Research Institute of Mechanics of the National Research Nizhny Novgorod State University, N. I. Lobachevsky, Nizhny Novgorod, Russian Federation
3Lobachevskii State University, Nizhny Novgorod, Russia
Corresponding Author:
V. S. Metrikin
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The results of a numerical-analytic study for the dynamics of a vibro-impact mechanism with a crank vibration generator are presented in this paper. We show bifurcation diagrams and stability regions that let us find basic patterns in the reorganization of motion modes when the mechanism’s parameters change.

1. Introduction

Invention [1] and schemes of mechanism prototypes shown their present a new scheme for vibro - impact mechanism with a crank vibration generator for earth compaction in a confined area of production. The scheme contains several percussion pistons, which lets one, as noted in [1], to perform earth compaction more efficiently, while small overall dimensions let one use the mechanism in complex confined condition. A similar scheme mechanism considered in [2-6]. In [2], a mathematical model for a vibro-impact mechanism with crank vibration generator is presented together with formulas for finding the simplest periodic motions of the mechanism.

The present work is a continuation of [2] and differs in that here we take into account that the considered scheme has a support plate for each percussion piston whose levels can be controlled to tune the mechanism for a specific desired operation mode. We also give results of numerical experiments that have let us find different types of the mechanism’s motion, including stochastic ones, and find values of parameters for which known period doubling bifurcations are realized.

1.1. Problem setting

The scheme of the considered mechanism is shown on Fig. 1(a), where 1 is the mechanism’s hull in which the bearings contain an axis 2 with a fly wheel 3 and cranks 4 and 5 with radii r1, r2 that have a stationary phase shift φ. The cranks have a joint connection to the piston rods 6 (of length li); percussion pistons 7 and 8 are, in turn, connected to them with a joint. Under the percussion pistons we have anvils 9, 10 with heights h1, h2 respectively. The hull 1 has a joint connection to the racks 11 that are rigidly connected to the anvil block 12. The rotation of the axis in the proposed scheme is transformed with a crank mechanism into a back-and-forth motion with respect to the anvil block. The percussion pistons may alternate their blows to the corresponding anvils, and the vibro-impact created here is transmitted through the anvil block to the material being compacted.

Fig. 1The scheme of the considered mechanism

The scheme of the considered mechanism

We denote by x the coordinate of the hull’s center of mass M, by xpi (i= 1, 2), coordinates of the percussion piston masses mi, and compose expressions for kinetic V and potential Π energies presenting the Lagrange function as:

L=12M x˙2+12i=13mix˙pi2 -Mg x-gi=13mixpi,

also, using obvious relations r1l, r2l, and assuming lil, i= 1, 2, we represent the mechanism’s motion equations as Eq. (1), (2):

d2xdτ2-μλ1cosτ-μγλ2cosτ-φ+p=0, x>fτ,
dxdτ+=-Rdxdτ-+1+Rdfτdτ, x=fτ, x˙-dfdτ<0,
fτ=maxτf1τ,f2τ, f1τ=k1+ε-μcosτ, f2τ=k1+Δk-μγcosτ-ϕ,

where we have introduced the following notation: τ=ωt, x=(xstar-s2-l)l-1, μ=r1l-1, γ=r2l-1,p=g(ω2l)-1,ε=(s1-s2)l-1,λi=mi(M+i=12mi)-1 (i=1, 2), while dx/dτ+=x˙+, dx/dτ-=x˙- are velocities immediately after and before the impact.

1.2. Solution method

Phase space for system Ф(xf(τ), x˙<+) in coordinates x, x˙, τ is reduced with respect to x. The surface S(x=f(τ)) is a cylindrical surface formed by an intersection of two surfaces x=f1(τ), x=f2(τ). All phase trajectories are located either on the surface S or above it. If x>f(τ) it corresponds to free motion of the mechanism; if x=f(τ), it corresponds to an impact interaction of one of the pistons with the stop (anvil block). Phase trajectories are shown on Fig. 2 in a qualitative form. In case of an impact motion for R0 the depicting point moves in the phase space Φ as follows: moving in the region G(x>f(τ)), it reaches the surface S at some point M0'(τ0,x0=f(τ0),x˙0) and then instantaneously moves along the surface S up to a certain point M0τ0,x0=f(τ0),x˙0+=-Rx˙0+(1+R)dfdττ=τ0 and then, having left S, moves according Eq. (1) in G until it reaches the surface S again at some point M1'(τ1,x1=f(τ1),x˙1). Thus, the depicting point will reach surface S every time.

The class of trajectories described above corresponds to a lengthy stop of one of the pistons or to successive “trampling” of the pistons. We must note that the form of the surface S shown on Fig. 2 is preserved only if surfaces S1 and S2 intersect.

Fig. 2The surface S

The surface S

However, it is clear that impact motions of the mechanism are possible if only one of the pistons interacts with the anvil. Then the surface S will be a smooth cylindrical surface with equation either x=f1(τ) or x=f2(τ). Using equations x=f1(τ), x=f2(τ) we can get a relation on the mechanism parameters:


Thus, the description of the phase space structure and the behavior of phase trajectories in it imply that as a section plane [7] we can take the surface S and study the dynamics with the method of point maps [7, 8]. In this case, it means mappings of the section plane S onto itself.

1.3. Constructing a point map


Mi(τ=τi, x=fiτi), x˙=x˙iSi, i=0,1,
M2(τ=τ2, x=f1τ2), x˙=x˙2S1,

be three consecutive points that belong to the surface S; then a transformation T=T2 T1 of the points M0T1M1T2M2 can be written as:

T1Δk-μγcos(τ1-φ)=-μλ1(cosτ1-cosτ0)-(τ1-τ0)(μλ1sinτ0 +μγλ2sin(τ0-φ))-μγλ2(cos(τ1-φ)-cos(τ0-φ))-p(τ1-τ0)22 +x˙0τ1-τ0+ε-μcosτ0, x˙1=-R(μλ1(sinτ1-sinτ0)+μγλ2(sin(τ1-φ)-sin(τ0-φ)) -pτ 1 -τ0+x˙0+1+Rμγsinτ1-φ,
T2ε-μcosτ2=-μλ1(cosτ2-cosτ1)-(τ2-τ1)(μλ1sinτ1 +μγλ2sin(τ1-φ))-μγλ2(cos(τ2-φ)-cos(τ1-φ)) -p(τ2-τ1)22+x˙1τ2-τ1+Δk-μγcosτ1-φ, x˙2=-R(μλ1(sinτ2-sinτ1)+μγλ2(sin(τ2-φ)-sin(τ1-φ)) -p(τ 2 -τ1)+x˙1)+(1+R)μsinτ2.

1.4. Existence and stability conditions for fixed points at a point map t corresponding to periodic two-impact motion modes

Equations for finding the coordinates of fixed points on a point map T corresponding to two-impact periodic motions (with consecutive impacts by each percussion piston) results by adding periodicity conditions [8] to Eq. (3-5):

x˙2+=x˙0+=x˙*, τ2=τ0+2πn, n=1,2,....

Resolving system Eq. (4-6) with respect to x˙, x˙1, τ0, τ1, we get:

x˙=(Rμ λ1(1+R)(sin(τ0+ξ)-sinτ0)+Rμ γ λ2(1+R)(sin(τ0+α)-sin(τ0-φ))
x˙1=(-Rμ λ1(1+R)(sin(τ 0 +ξ)-sinτ0)-Rμ γ λ2(1+R)(sin(τ0+α)-sin(τ0-φ))
α=ξ-φ, ξ=τ1-τ0.

1.5. Results of numerical experiments

Our study of the mechanism’s complex dynamics has been augmented by numerical experiments that employ a software suite developed in the Borland C++ Builder 6 IDE. We denote by D(m1,m2)the existence and stability region for periodic motions in the space of parameters, where m1 and m2 denote the number of impacts by the first and second percussion piston against the anvil block respectively. Fig. 3 shows the bifurcation diagram built for of parameters (μ=0.12, ε=0.018, γ=3, φ=3.14, λ1=0.2, λ2=0.3, k1=0, k2=0). The horizontal axis on the diagram shows the values of the frequency parameter p; the vertical axis, values of post-impact velocities x˙i+f(τ). Fig. 3(a) corresponds to the diagram with impacts by first piston x˙i+f1(τ); Fig. 3(b), to the diagram with impacts by the second piston x˙i+f2(τ).

Fig. 3Bifurcation diagrams

Bifurcation diagrams

a) For the first piston

Bifurcation diagrams

b) For the second piston

Fig. 4Areas of the existence and stability of periodic motions with alternating strokes of the pistons: a) k1=0, k2=0, b) k1=0.2, k2=0.3

Areas of the existence and stability of periodic motions with alternating strokes  of the pistons: a) k1=0, k2=0, b) k1=0.2, k2=0.3


Areas of the existence and stability of periodic motions with alternating strokes  of the pistons: a) k1=0, k2=0, b) k1=0.2, k2=0.3


The pictures show that for frequencies 0.135p0.2 there exists a periodic motion with m1=1, m2=1; for frequencies 0.13p0.135, periodic motion modes with m1= 1, m2= 0 (there occur periodic strikes by only one piston); for frequencies 0.12p0.13 we observe periodic motion modes with two strikes of only one piston (m1= 2, m2=0); with four (0.118p0.12m1= 4, m2=0) and, finally, in the interval 0.1p0.118 we see a chaotic motion mode. Values of frequencies p=0.12 and p=0.13 are bifurcational since as their values increase, we see that the number of strikes by the first piston doubles (the period doubling process), which is known to lead to chaotic motion [9]. With our software suite, we performed numerous computations, in particular, constructed existence and stability regions for periodic motion modes as a function of the relative value of the supports for percussion pistons. For instance, Fig. 4(a) shows, in the plane p,R, the region D1,1 (dashed region) for the following set of parameters (without supports):

μ=0.12, ε=0.018, γ=3, ϕ=3.14, λ1=0, λ2=0, k1=0, k2=0,

and the bifurcation boundary Nc [8]. In the region D(m1,m2), where m1 and m2 are not simultaneously equal to 1, there exist motions with several (more than two) strikes by each of the pistons. Fig. 4(b) shows the existence and stability region for the periodic motion (m1= 1, m2= 1) for the values of parameters shown above with relative support height k1= 0.2, k2= 0.3. This figure indicates that the use of supports for percussion pistons lets us extend the range of parameters in order to tune the mechanism for a certain stable motion mode.

2. Conclusions

The proposed numerical-analytic method of study (based on the method of surface point maps) for the dynamics of new kinds of vibroimpulsive mechanisms has let us find regions in the space of parameters (#(3)) useful for successful tuning and control for the mechanism’s motion, while our numerical computations imply the possibility for a specific choice of parameters and illustrate the basic reorganizations of the mechanism’s motion modes depending on the changes in parameters.


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About this article

12 June 2016
03 September 2016
07 October 2016
Mechanical vibrations and applications
point mapping
bifurcation diagram
coefficient of restitution
impact interaction

Development of mathematical model is financially supported by Russian Science Foundation, Project No. 16-19-10237. Investigation of numerical results was financed within the framework of the base part of State Task of the Ministry of Education and Science Project No. 2014/134 2226.