Vibro-Engineering and the Technology of Piling and Boring Work
	Authors: Mikhail Grigorevich (M.G.) Tseitlin Vladimir Vladimirovich (V.V.) Verstov Gennady Grigorevich (G.G.) Azbel	Publisher: Stroiizdat, Leningrad Otdelenie Leningrad, 1987 Table of Contents

Calculation of the parameters of longitudinal-action vibrational pile drivers.

The initial data for calculation are: the mass of the element to be driven m_o, in kg; the geometric dimensions of the element to be driven;the depth of sinking l, in m; and the soil conditions.

1. The resistance of the soil is determined. The calculated value FCR of the critical separation resistance at a given maximum sinking depth (kN) is determined on the basis of the original data characterizing the soil conditions:

where i is the ordinal number of the soil layer of thickness l_i passed through during the sinking, k is the total number of layers and Z is the perimeter of the cross section. The values of the specific separation resistance σ are assumed according to the data of Table 5.

2. After determination of the tentative mass value m_o, in kg, of the element to be driven and the parts of the vibratory pile driver rigidly connected with it, the approximate value of the static moment of the mass of the eccentrics, in kg • m, is calculated:

where ψ = 0.8 for reinforced concrete piles and ψ = 1 for the other elements sunk.

The recommended vibrational amplitude A_o required for an effective sinking is determined with the data of Table 6.

3. The frequency of the vibrations of the vibratory pile driver, Hz, is calculated as follows:

When the set of parameters of the vibratory pile driver is derived with a previously undetermined interval of change in the θ value, it must be determined from the condition

The amplitude of the vibration velocity v_o for a successful sinking should be within the interval of 0.5-0.8 m/s ; אַ is a coefficient that takes the resilience of the soil into account: אַ = 0.6-0.8 for low-frequency vibratory pile drivers (5-10 Hz) and אַ = 1 for the others. If the value θ is determined by this method, the static moment of mass of the eccentrics is calculated with the formula, in kg • m:

4. The required minimum mass of the vibratory pile drive and driven element, in kg, is determined as follows:

where U_c is the cross sectional surface, in cm²; p_o are the recommended pressure values required; the dependence of the pressure p_o, in MPa, on the type and dimensions of elements driven into water-soaked sandy and loose clayey soils is given below:

5. The value of the ratio of the force of gravity to the amplitude of the compelling force P_θ is verified:

	v1	v2
for a steel sheet pile	0.15	0.5
for light piles	0.3	0.6
for heavy piles and tubular ones	0.4	1.0

In performing the calculations with respect to this point, either the mass m_o or the amplitude of the compelling force (due to an increase in K or θ) is increased if necessary.

6. Finally, the values K, θ and m_o are precisely defined, after which these parameters are verified with the formulas:

In addition, the precisely defined parameters are verified with the formulas of paragraphs 4 and 5.

7. The power of the driving motor is determined by:

where D is the diameter of the journals of the shafts of a vibration exciter, in cm.

The efficiency of transfer from the motor to vibration exciter (equal to 0.9), the coefficient of rolling friction in the bearings of the vibration exciter (equal to 10^-3), and the additional consumption of power in the vibration of the soil mass, assumed to be 15% of the power expended to overcome the resistance of the soil, were studied here.

Calculation of the parameters of longitudinal-action impact-vibration hammers.

The original data for the calculation are the same parameters as for the vibratory pile drivers.

1. On the basis of the original data on the element driven, the mass of the impact part of the vibratory hammer is determined, in kg:

m₁ =(0.7 — 1.2)m₂.

2. The amplitude value of the compelling force, kN, is determined:

P_o = dm₁ x 10^-2.

The lower limit of the parameter d (d = 2-6) is designated for impact-vibration hammers that drive elements with a relatively small cross sectional surface (up to 50 cm²). The parameter d also increases with an increase in cross sectional surface.

3. The preliminary depression force of the working springs is calculated, in kN:

The parameter sin α = 0.3 - 0.5. An attempt must be made to assure the value sin α = 0.4 in designing the hammers.

4. The static moment of mass of the eccentrics is determined, in kg • m:

K = 25.3 P_o/θ².

The frequency of the compelling force of the hammer θ lies within the interval of 6-10 Hz.

5. The optimal stiffness of the working springs of the vibratory hammer is, in N/cm:

c₁ = (3.5 - 10) x 10^-2 m₁ θ²

In designing the hammers it is desirable to obtain the minimum c₁, value from the recommended optimal range.

6. The ratio γ₁ between the frequency of the natural vibrations of the impact part and the frequency of the compelling force:

7. The dimensionless resistance of the soil f and γ is calculated with the F and R values (9). The existence of an impact-vibrational mode is verified in terms of the parameters, sin α, γ₁, and f + γ (see Figure 22).

8. The dimensionless impact velocity is calculated (correlation formula):

9. The velocity of the impact part at the moment of impact is determined, in m/s:

x_imp = 6.28 x K θ/m₁ y₁

With respect to the durability of the hammer, the impact velocity should not exceed 2 m/s. If the value x_imp » 2 m/s with the parameters chosen, it is necessary to select other parameters that assure a value x_imp ≤ 2 m/s

10. The dimensionless sinking per impact (correlation formula)

11. The possibility of driving under the given soil conditions is checked:

The value Δ_L is adopted according to the data (Yu. R. Perkov, V. N. Shaevich, 1974) given below:

If it turns out that x_PL < Δ_L, it is necessary to reduce the parameter sin α to 0.2-0.3 and repeat the calculation. When x_PL again proves to be less than Δ_L, it can be assumed that the impact vibrational driving is ineffective under the given soil conditions.

12. The dimensionless rising height of the impact part is calculated:

13. The maximum rise value of the impact part is determined, in cm:

14. The maximum reaction of the vibratory hammer springs is calculated, in kN:

15. The drive engine power required is calculated, in kW:

The transfer efficiency from the vibration exciter to the motor (equal to 0.9) and the friction coefficient in the supports of the shafts (equal to 10^-3) are taken into account in this formula.

The selection of the parameters of the the impact -vibrational machines for extracting the elements from the soil is done by the same method, but in this case, in kN,

Calculation of the parameters of longitudinal-rotatory-action vibratory pile drivers.

The initial data for the calculation are the same characteristics as for longitudinal-action vibratory pile drivers.

1. The basic calculation characteristics of the driving system are determined:

where σ_P,V is the specific resistance on the lateral surface of the shell being driven with longitudinal-rotational vibrations; the σ_P,V values are given in Table 7, compiled according to the results of experimental studies:

where U_t is the area of the end surface of the shell, in m₂ ; R is the calculated resistance of the soil under the end of the shell, in kPa (undertaken according to the data of SNip 11-02 — 03.85).

2. The required dimensionless velocity values of the vibrations are determined:

where v_n is the projected driving velocity in m/min (recommended value: v_n = 0.2 -1.0 m/min) ; v_n = v_o/a² ; θ is the frequency (recommended value: θ = 6-7 Hz).

3. The amplitudes of the compelling force and the static moment of mass of the eccentrics are determined, in kg – m:

4. The separation conditions of the shell relative to the adjacent soil are verified:

The A_min values are given in Table 8.

5. The magnitude of eccentricity of application of the compelling force is determined:

The δ value is selected as a function of the ratio of vibrator mass m₁ and the mass of the driven shell m₂;

6. The drive power of the vibratory longitudinal-rotational action pile driver is calculated, in kW:

where D is the diameter of the support of the eccentric shaft, in mm; η_ver is the coefficient that takes into account the losses in transfer from the engine to the eccentric shafts.

7. It is recommended that the effort in extracting the tubular element from the soil under the action of longitudinal-rotational vibrations be determined with the formula

S = 10 m_o + F_H3

where F_H3 is the mean force required to overcome the lateral resistance of the soil during vibratory extraction: F_H3 = ζF_e; F_e is the separation resistance along the lateral surface of a tubular element; and ζ is the coefficient of decrease in the lateral resistance as a function of the vibratory mode.

The ζ value is determined by the graphs plotted with Equation (35) and given in Figure 19, as a function of the ratio of the extraction velocity (v_H3) to the amplitude of the velocity of the longitudinal component of the vibrations (Aω). The rate of rise in the tube should not exceed 0.5-1.0 m/min in the first extraction stage.