RU2488798C2 - Automatic method of fatigue test of two pairs of double-span bridge rails with wheels of bridge cranes - Google Patents

Abstract

FIELD: construction.

SUBSTANCE: automatic method includes fatigue testing of two pairs of double-span bridge rails by wheels of two bridge cranes. Walls of upper and lower pairs of rails are inclined at the angle α to the vertical line and are fixed with turn-buckles relative to each other, rails are fixed to the lower pair of rails at the bottom, and at the upper pair on the top they install cylindrical coaxial hinge joints that respond to each other to the lower pair on the top, and to the upper pair on the bottom, and a single joint of rails is produced. A lower bridge crane is mounted into a bench with eight wheels upwards, the joint of rails is rested against eight wheels of the lower crane, a connecting rod is hingedly connected to the joint of rails. A double cantilever girder is mounted on the frame of the upper crane with eccentricity, traction dynamometers are suspended to its protruding cantilevers, and using the eccentricity value, they control amplitudes of oscillations of shifting stresses in ten underneath zones of the rails. Asymmetrical rails are suspended to dynamometers, with eccentricity towards a flywheel, anchor traction rods are suspended at the ends of each asymmetrical rail and connected to the frame and the foundation of the bench. Upper and lower eight-wheel cranes are tightened to each other, the joint of rails is pressed between wheels of these cranes with the rated eccentricity, and automatic reciprocal oscillations are sent by the connecting rod.

EFFECT: automation of the method for fatigue testing of bridge rails, expansion of functional capabilities, increased stability of operation and simplified design of a bench.

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Description

The present invention relates to building structures, namely to crane with intensive, heavy duty 8K, 7K overhead cranes, as well as to bridge structures. And their endurance tests by cyclic movable influences of the wheels of bridge cranes, by millions of cycles of their rolling.

Known stands for cyclic endurance tests proposed by K.K. Nezhdanov and developed together with graduate students [1], [2], [3], [4], [5], [6], [7], [8]. They are designed for endurance testing of blocks of two split beams and simulate all moving concentrated impacts of the wheels of bridge cranes:

vertical P, horizontal T and torques M _cr . We take well-known solutions for analogues. The lack of analogues is the inability to test continuous crane beams.

A well-known stand for endurance testing, designed to test a bunch of four continuous crane beams, proposed by K. K. Nezhdanov and designed with graduate students [8]. This stand simulating cyclic moving concentrated impacts of wheels of two bridge cranes. We will take this closest technical solution also as an analogue [8]. In an analogue, the effects of the wheels are created by hydraulic jacks, which complicates the construction of the stand. The automatic endurance test method for two pairs of continuous crane beams [8] can be greatly simplified.

For the prototype we will take the closest technical solution, a stand for cyclic endurance tests of continuous beams, proposed by K. K. Nezhdanov and developed together with graduate students in the application for invention [9]. Currently, this technical solution has been implemented, and this stand is operated in the laboratory "Endurance of transport structures" PTU AS.

The relevance of endurance tests of continuous continuous crane beams is high, since the endurance limits for the rail sections of the walls of continuous continuous crane beams have not yet been obtained! At the same time, the material consumption of continuous crane beams is 28 ... 30% less than split. The straightening of rail marks on continuous crane beams is also greatly simplified [10, 11]. The absence of endurance limits for under-rail zones of the walls of continuous crane beams restrains their widespread use for crane structures.

It is most convenient to test the endurance of two pairs of continuous double-span crane beams, combined into a single bundle (hereinafter, the term continuous is meant and omitted). During the tests, it was found that in the under-rail zones subjected to cyclic influences of the crane wheels, it is easy to control the amplitude of the shear stress oscillations, which facilitates the construction of regression dependencies [11], and also the possibility of increasing the reliability of the entire structure was clarified.

The technical result of the invention is the automation of the method of testing double-span crane beams for endurance, by regulating the amplitudes of oscillations of local stresses in the under-rail zones, expanding the functionality of the stand, increasing the stability of its operation and simplifying the design of the stand.

The technical result on the implementation of the automatic method of endurance testing of a bunch of two pairs of double-span crane beams by the wheels of two bridge cranes in the stand is achieved as follows.

The walls of the upper and lower pairs of the said beams, to simulate an oblique bend, are tilted at an angle α to the vertical and fixed with lanyards relative to each other.

The rails are attached to the lower pair of beams from the bottom, and to the upper pair from the top, mount coaxial cylindrical joints that respond to each other, to the lower pair from the top, and to the upper pair from the bottom.

They combine the hinges, form a single bundle of beams, mount the lower bridge crane with eight wheels upwards in a stand and attach it with anchor bolts to the foundation.

Leaning a bunch of beams with rails on eight wheels of the lower crane, pivotally attached to a bunch of beams, connecting rods, longitudinal reciprocating vibrations.

Mount the upper eight-wheel crane, rest its wheels on the guide rails of the bundle of beams and motionlessly fix it in relation to the foundation of the stand by ties.

The difference is that on the frame of the upper crane the two-console beam is mounted with eccentricity, towards the flywheel relative to the center of the upper crane.

Suspension dynamometers are suspended to its protruding consoles and the magnitude of the eccentricity of the double-beam installation is controlled by the oscillation amplitudes of the shear stresses in ten sub-rail zones of the beam bundle.

They install bolts securing the dynamometers, hang uneven beams with eccentricity towards the flywheel to the dynamometers, hang the anchor rods at the ends of each uneven beam and connect them to the frame and the base of the stand, and the nuts of the anchor rods interact through the thrust bearings with the washers, and the washers with the springs compression.

Tighten the nuts to the design value with a torque wrench, control the force with dynamometers, tighten the upper and lower eight-wheel cranes with each other, clamp a bunch of beams between the wheels of these cranes, with the design eccentricity.

The crank informs the automatic reciprocating vibrations of the beam bundle and the cyclic operation of the stand, with a given amplitude, with the automatic inclusion of emergency multi-channel protection, adjusts the gap between the fixed reed switch and magnets attached to the oscillating beam bundle.

In automatic mode, each of the ten sub-rail areas of the beams is tested, registering the cycles with a counter operated by a reed switch and disconnecting the stand when the magnetic gap increases abnormally, the stand is operated, and the under-rail areas of the beams are tested until fatigue cracks appear in them on the basis of millions of cycles of rolling the crane wheels.

$${\sigma }_y^{loc},$$

$${\tau }_{xy}^{loc},$$

$${\sigma }_1^{loc},$$

$${\sigma }_2^{loc},$$

$${\tau }_{\mathrm{1,2}}^{loc},$$

$${\tau }_{2\max }^{loc}$$

по известным формулам «Теории упругости», а затем производят статистическую обработку результатов усталостных испытаний подрельсовых зон стенок и получают линии регрессии и пределы выносливости для исследуемого типа подкрановых балок в зависимости от колебаний величин сдвигающих напряжений в подрельсовых зонах стенок [10, 11]. Исследования проводятся на базе шести миллионов прокатываний колес кранов.Fluctuations in local stresses in ten sub-rail zones of the beam walls are recorded in a known manner by strain gauges [10, 11], by gluing strain gauge sockets in the under-rail zones. Using a loop oscilloscope or strain gauge station, the relative deformations ε _x , ε _y , ε _{45 °} are recorded in the under-rail zones. According to the developed program, oscillations of all local stresses are obtained $${\sigma }_x^{loc},$$

$${\sigma }_y^{loc},$$

$${\tau }_{xy}^{loc},$$

$${\sigma }_{\mathrm{one}}^{loc},$$

$${\sigma }_2^{loc},$$

$${\tau }_{\mathrm{1,2}}^{loc},$$

$${\tau }_{2\max }^{loc}$$

according to the well-known formulas “Theory of elasticity”, and then statistical processing of the results of fatigue tests of the under-rail zones of the walls is carried out and regression lines and endurance limits for the type of crane beams under study are obtained depending on fluctuations in the values of shear stresses in the under-rail zones of the walls [10, 11]. Research is conducted on the basis of six million cranes wheel rolling.

Figure 1 shows a stand - General view; figure 2 is a section aa; figure 3 is a view of B in figure 2; figure 4 - node swivel of two-span beams in a single bundle and a swivel connecting rod connecting the bundle of beams reciprocating oscillations.

The endurance test bench for ten under-rail zones in double-span crane beams is installed on the foundation 1. The frame 2 of the stand is fixedly rigidly attached to the foundation 1 with anchor bolts 3.

Each pair of wheels 4 of the bridge cranes forms a balancing trolley 5. Four balancing trolleys 5 are fixedly mounted on the crane frame 2 at a distance “B” (base distance) with the possibility of changing the base distance “B” and the number of balancing trolleys 5 [8, 9]. Four two-wheeled balancing trolleys 5 imitate the lower 6 overhead crane, facing upwards with eight wheels 4. The plane of the wheels 4 are parallel to each other.

Guide rails 7 are mounted on the lower belts of the lower pair of double-span beams 8. By means of these rails 7, the lower 8 pair of double-span beams is supported on the balancing trolleys 5 of the lower 6 bridge crane.

Three pairs of coaxial joints 9 connect the lower 8 pair of two-span beams with the top 10 pair of two-span beams in a single bunch of beams. At the same time, guide rails 11 are also fixed on the upper belts of the upper 10 pairs of double-span beams, on which the upper eight-wheeled bridge crane 12 is supported by its wheels 4. That is, the bridge crane 12 is supported by a two-track rail.

On the frame 13 of the upper bridge crane 12, a two-console 14 (box-shaped) beam with two consoles protruding outward is supported from above.

Double-beam 14 beam rests on the frame 13 of the upper bridge crane 12 and is offset relative to its center by the amount of eccentricity e to the flywheel.

Fifty-ton tensile dynamometers 15 are suspended from the consoles of the two-console 14 beam. Increasing the amount of eccentricity e in the direction of the flywheel, we increase the impact of the wheels of the cranes on the side of the flywheel and vice versa.

Dynamometers 15 are suspended from the consoles of the two-console beam 14 by means of nuts 16 with a spherical bearing surface. Each nut 16 interacts with this supporting surface with a spherical hole in the supporting washer 17, based on the console of the two-console beam 14.

The lower nuts of the dynamometers 15 are similar to the upper nuts and are placed in the sleeves 18. To the sleeves 18 on the rods 19 are suspended unequal 20 beams.

This device is designed to tighten the upper and lower bridge cranes and clamp between the wheels of the cranes a bunch of double-span beams. A loading device is placed between the upper and lower bridge cranes.

Increasing the eccentricity e , we increase the impact of the wheels of the bridge cranes on the flywheel side. One shoulder of the unequal arms 20 of the beam on the flywheel side is shorter than the other shoulder.

Each non-shoulder 20 beam is supported from below by a washer 21 with a spherical hole. The fixing nut 22 also has a spherical contact surface.

Anchor bolts 23 are passed through the ends of each unequal beam 20. The lower ends of the anchor bolts 23 are fixedly connected to the frame 2 and the stand foundation.

Anchor bolts 23 protruding upward from unequal beams 20 are fitted with compression springs 24 (from a steam locomotive).

The washers 25 are laid on the springs 24, and the thrust bearings 26 are laid on the washers. The thrust bearing is pressed against the spring 24 by the anchor nut 27. The other end of the uneven beam 20 is fixed motionless by the anchor nut 27. The load is created by guaranteed tightening of the anchor nuts 27 with a calibration wrench. When tightening the anchor nut 27 with a calibration key, the pulling force of the pull rod 19 is doubled.

The magnitude of the effects of the wheels 4 of the upper 12 and lower 6 of the eight-wheeled bridge cranes is controlled by dial gauges built into the fifty-ton tensile dynamometers 15. The unequal beams 20 distribute the vertical effects on the wheel balancers inversely proportional to the shoulders of the unequal beams 20.

Changing the magnitude of the eccentricity e , we control the distribution of effects between the balancing trolleys of the cranes.

In the current stand, the amplitude of the vibrations of the bundle of beams is 350 mm, the amplitude of oscillations is 700 mm.

The frame 13 of the upper bridge crane 12 is connected by horizontal ties 28 to the frame of the mechanism of longitudinal reciprocating vibrations of a bunch of beams with a given amplitude and amplitude of oscillations. These connections 28 accurately capture the design position of the upper bridge crane 12.

The mechanism for generating reciprocating vibrations [8, 9] is connected by a flywheel connecting rod 29 to a pair of upper 10 and a pair of lower 8 beams, whose walls 15 are inclined at an angle α = 5 ... 6 ° to the vertical. By changing the angle of inclination α, we adjust the oblique bending of each two-span beam. All beams form a single bundle.

A single bunch of beams performs reciprocating vibrations with a given amplitude (350 mm) and frequency between the wheels of the upper and lower eight-wheeled bridge cranes. The frame 13 of the upper bridge crane 12 is connected through dynamometers 15, rods 19, unequal beams 20 and springs 24 with anchor bolts 23.

In the tested bunch, the two-span beams 8 and 10 are parallel to each other (see figure 2.). Rails 7 and 11 are mounted on the belts of two-span beams with or without eccentricity. In the current stand, the carrying capacity of each tensile dynamometer 15 is 50 tons (49.05 gN).

The double-console beam is mounted on the upper crane and, therefore, a pair of tensile dynamometers 15 acts on the cranes with an eccentricity e .

The inclined installation of the tested pairs of double-span beams 8 and 10 to the vertical provides an imitation of the horizontal braking forces T of the cranes [8, 9] and the oblique bending of the tested two-span beams 8 and 10, connected to each other by ties (shown schematically).

The hinges 9, on the tested two-span beams, are aligned with each other, and form three pairs of hinges 9 (see figure 2.)

Figure 1 shows the upper bridge crane 12, supported by eight wheels 4. Can be installed and a bridge crane, supported by four wheels. The lower bridge crane 6 is facing eight wheels 4 up.

The mechanism of longitudinal reciprocating vibrations applied the previous [1, 2, 3, 4, 5, 6, 7, 8, 9] (not shown). It provides oscillations of the tested beams with a given amplitude a = 350 mm and a span of 700 mm.

Communication 28 exclude spontaneous longitudinal movements of the overhead crane 12 with respect to the fixed foundation 1 of the stand. Communication 28 perceive horizontal forces arising from the operation of the mechanism of longitudinal reciprocating vibrations.

The massive flywheel (a wheeled pair from the Sergo Ordzhonikidze steam locomotive) accumulates the kinematic energy of the longitudinal reciprocating vibrations and protects the electric motor from overloads. The flywheel connecting rod 29 informs the two pairs of double-span beams 8 and 10 of the oscillation with a given amplitude and frequency.

The reciprocating movements of the bundle of beams provide a complete simulation of the cyclic rolling of the wheels of two bridge cranes 6 and 12, as in real operating conditions.

Figure 1 shows three hinges 9 mounted on the test beams. The hinges 9 are mounted coaxially (see figure 2.).

In the case shown in Fig. 1, the operation of double-span crane beams of the workshop is simulated. The number of pairs of hinges 9 can be increased or decreased. Between pairs of hinges 9, the same or different spans can be fixed.

If the number of pairs of hinges 9 is reduced to two, the operation of split beams is simulated. The pairs of hinges 9 can be installed either at the very edge of the bundle of beams, or at some distance from its end (the work of a double-beam beam is simulated).

The stand is mounted and launched into automatic operation as follows.

Mount the frame 2. Then mount the balancing trolley 5 and set the design distance between them (base B).

Four tested two-span beams are connected in parallel to each other in a single bunch of beams. The connecting lanyards of the bundle of beams allow you to adjust the distance between their longitudinal axes.

The installation of two-span beams at an angle α = 5 ... 6 ° to the vertical provides an imitation of the horizontal braking forces T acting on them. By changing the eccentricity and the installation of the double-console beams, the vertical forces of the wheels of the balancing trolleys on the test beams are regulated.

On the bottom 8 pair of double-span beams, the rails 7 are fixed below, and the hinges 9 above. On the upper 10 pair of double-span beams, on the contrary, the rails 11 are fixed at the top, and the hinges 9 at the bottom.

The connecting rod 29 provides longitudinal reciprocating vibrations of a bunch of beams with a given amplitude and frequency of oscillation. The upper pair of two-span beams is lowered from above and fixed by hinges 9 on the lower pair of two-span beams 8.

The bridge crane 12 is mounted in the assembly and supported by eight wheels 4 in pairs of combined balancers 5 on the rails 11 of the upper pair 10 of two-span beams. Then, the bridge crane 12 is fixed in the longitudinal direction by ties 28 connecting it to the frame of the mechanism of longitudinal reciprocating vibrations (not shown).

The compressive forces are transmitted by eight wheels of the upper 12 bridge crane to the upper 10 pairs of double-span beams. Then, through the hinges 9 to the lower pairs of double-span beams 5 and then to the eight wheels of the lower crane 6.

The forces of the effects of the eight wheels of the upper 12 bridge crane, directed from top to bottom, are mutually balanced by the response forces of the effects of the eight wheels of the lower 6 of the bridge crane, so only gravity from the mass of the stand is transmitted to the foundation 1 of the stand. Significant internal efforts in the stand are mutually balanced.

Then the mechanism of longitudinal reciprocating vibrations is turned on, and the connecting rod 29 informs the beam bundle of cyclic vibrations with a given amplitude of 350 mm.

Each top 10 two-span beam is tested for endurance in three under-rail areas under the wheels of each balancing trolley 5 and in the interval between two balancing trolleys. That is, each top 10 two-span beam is equivalent to testing three beams. Moreover, the wheels of the balancing trolleys closest to the flywheel are the most loaded, and the wheels of the balancing trolleys most remote from the flywheel are the least loaded. Each lower 10 two-span beam is tested for endurance in two under-rail zones - equivalent to testing two beams.

The passage of the bundle of beams in one direction provides one cycle of oscillation of the bundle of beams in one direction, and causes one cycle of oscillations in each studied section (six at the top and four at the bottom).

The number of revolutions of the flywheel is 36 per minute.

The number of cycles per minute in each of the sections is twice as large - 72.

The number of cycles in each of the sections is 103680 per day.

The number of under-rail zones tested for endurance is ten.

It is easy to determine the total productivity of the stand per day 103680 · 10 = 1036800 cycles. High performance!

Typically, in workshops with intensive heavy duty (8K, 7K), 0.8 ... 0.7 million cycles [10], [11] of rolling crane wheels per year are accumulated.

Concrete implementation example

Figure 5 shows a diagram of the effects of the wheels of the upper and lower eight-wheeled bridge cranes. Two compressive forces 2F = 2 × 1500 gN act on each of the cranes. Each of the forces P = 1500 gN is applied to the upper crane with an eccentricity “ ^e ” = 10 cm towards the flywheel.

The distance between the axles of each of the four wheels of the upper bridge crane (wheel formula) is 50 + 50 + 50 = 150 cm. The dimension between the extreme wheels is 150 cm.

As a result of applying the force F = 1500 gN with an eccentricity e = 10 cm, the forces at the upper crane were distributed as follows: the shoulder from the force to the center of the balancer decreased to 50-10 = 40 cm from the force, and from the force to the center of the balancer to 50+ 10 = 60 cm. On the right balancer 900 gN (100%), and on each of its wheels 450 gN (100%). On the left balancer is 600 gN (66.7%), and on each of its wheels 300 gN (66.7%).

Lower bridge crane

The distance between the axles of each of the four wheels of the lower bridge crane (wheel formula) is 50 + 100 + 50 = 200 cm. The distance between the centers of the lower balancers is 150 cm, and between the extreme wheels is 200 cm.

As a result of applying the force F = 1500 gN with an eccentricity of e = 10 cm, at the lower bridge crane, the forces between the wheels are distributed as follows: from the force F = 1500 gN to the center of the balancer on the right is 75-10 = 65 cm, and to the center of the balancer on the left is 75 + 10 = 85 cm. On the right balancer 850 gN (94.4%), and on each of its wheels 425 gN (94.4%). On the left balancer, 650 gN (66.7%), and on each of its wheels 325 gN (72.2%).

That is, the eccentricity e of the suspension of the dynamometers controls the magnitude of the vertical and horizontal effects of the wheels of the balancer trolleys on the test beams.

Comparison with the analogue shows significant differences between the developed stand. The stand allows you to simultaneously test endurance under identical conditions, a single bunch of beams both continuous and split, and each upper two-span beam is tested in three zones and, therefore, it is equivalent to testing three beams. Each lower beam is tested in two zones and, therefore, it is equivalent to the tests of two beams.

The economic result arises from increasing the reliability of the tests, since the loading condition for double-span beams is the same as in the existing workshops. The application of force F with an eccentricity to the upper and lower cranes ensures control of the magnitude of the vertical and horizontal impacts of the wheels on the test beams in all ten test zones. Tests continue until fatigue cracks appear in most or even all ten sub-rail areas of the test beams. That is, with one tab in the stand of beams of a certain type, we get ten experimental points and, statistically processing the test results in a known manner [10, 11], we obtain regression lines and endurance limits for the type of crane beams under study.

The stand provided an imitation of the operation of continuous crane beams of two adjacent spans of the workshop, as well as split.

The stand is operated in the laboratory "Endurance of transport structures" Penza State University of Architecture and Construction. The reliability of the stand is higher compared to previous stands. The stand is equipped with emergency multiple protection and can be operated around the clock, continuously in automatic mode.

Item Numbers

1. foundation

2. stand frame

3. anchor bolts

4. a pair of wheels

5. balancing trolley

6. bottom crane, facing eight wheels 4 up

7. rails

8. a pair of lower beams.

9. hinges

10. a pair of upper beams

11. guide rails

12. upper bridge crane

13. frame of the upper bridge crane

14. double-console box beam

15. tensile dynamometers

16. nut with a spherical surface

17. washer with spherical recess

18. sleeve

19. traction

20. unequal beam

21. washer with spherical recess

22. nut with a spherical surface

23. anchor bolts

24. compression springs 22

25. washers

26. thrust bearings

27. anchor nuts

28. horizontal connections

29. connecting rod of the mechanism of reciprocating oscillations

30. swivel connecting rod.

Bibliography

1. Nezhdanov K.K. The test bench for endurance beams, and.with. No. 0840679, USSR. M. Cl. ³ ЕВВ 9/48. // Bull. No. 44 - 1981.

2. Nezhdanov K.K. Endurance test bench: Patent of Russia No. 840679 M. Kl. G01M 5/00, valid from 8/10/1993

3. Nezhdanov K.K., Nezhdanov S.K., Chumakov V.A. The stand for mechanical tests of beam building structures, and.with. No. 1416872, USSR, M. Cl. ⁶ 01M 5/00 // Bull. No. 30 - 1988.

4. Nezhdanov K.K., Nezhdanov S.K. and others. Endurance test bench: Patent of Russia No. 1677583, G01N 3134 is valid from 10.27.1993.

5. Nezhdanov K.K., Nezhdanov S.K. and others. Stand for testing crane beams for endurance: A. with. No. 1686335, USSR, M. cl. G01M 17/00 // BI - 1991. - N 39.

6. Nezhdanov KK, Krylov II, Chumakov VA, Vasyuta B.N. Endurance test bench: A.S. No. 1418586, USSR, M. Cl. G01M 5/00 // Bull. No. 31 - 1988.

7. Nezhdanov K.K., Tumanov V.A., Nezhdanov A.K., Maskaev A.S., Lashtankin A.S. Stand for cyclic endurance test of beams with moving torques. Russian Patent No. 2213334. M., Cl. G01M 5/00. Bull No. 27. Zareg. 09/27/2003.

8. Nezhdanov K.K., Tumanov V.A., Nezhdanov A.K., Tikhonov K.B. Test stand for crane endurance beams. Patent of Russia No. 2191363. M., Cl. G01M 3/20. G01N 3/20. Bull No. 24. Zareg. 10/20/2002.

9. Nezhdanov K.K., Nezhdanov A.K., Kurtkezov D.Kh. An automatic method of endurance testing of four two-span crane beams. Application for invention No. G01M 19/00, G01N 3/20. 2009-02-05 (prototype).

10. Nezhdanov K.K. Improvement of crane structures and methods for their calculation. The dissertation for the degree of Doctor of Technical Sciences. Penza, 1992.

11. Nezhdanov K.K. Improvement of crane structures and methods for their calculation [Text]: Monograph. - Penza: PGUAS, 2008.288 s.

Claims (1)

An automatic method of endurance testing of two pairs of double-span crane beams by the wheels of two bridge cranes, the walls of the upper and lower pairs of the said beams being tilted to simulate oblique bending at an angle α to the vertical and fixed with lanyards relative to each other, the rails are attached to the lower pair of beams from below, and to the upper pair from the top, mount cylindrical coaxial joints that are reciprocal to each other, on the lower pair from the top, and on the upper pair from the bottom, combine the hinges, form a single bunch of beams, mount eight wheels in the stand upside down the lower bridge crane and attach it with anchor bolts to the foundation, rest the beam bundle with rails on eight wheels of the lower crane, pivotally connect the connecting rod of the longitudinal reciprocating vibrations to the beam bundle, mount the upper eight-wheel crane, resting its wheels on the guide rails of the beam bundle, and motionlessly fix it with respect to the foundation with ties, characterized in that a double-beam beam with eccentricity is mounted on the frame of the upper crane, towards the flywheel relative to the center of the upper crane they hang tensile dynamometers to its protruding consoles and adjust the amplitude of the shear stress oscillations in the ten sub-rail areas of the beams with the size of the eccentricity, mount the bolts, the safety dynamometers, hang uneven beams with the eccentricity towards the flywheel to the dynamometers, hang their uneven arms and hang on the ends of each the frame and the base of the stand, and the nuts of the anchor rods interact through thrust bearings with washers, and the washers with compression springs, with a torque wrench they tighten the nuts to the design value, control the magnitude of the forces with dynamometers, tighten the upper and lower eight-wheel cranes with each other, clamp a bunch of beams with a design eccentricity between the wheels of these cranes, tell the connecting rod automatic reciprocating vibrations to the bunch of beams and the cyclic operation of the stand with a given amplitude, with automatic inclusion of emergency multi-channel protection, adjust the gap between the fixed reed switch and the magnets attached to the oscillating beam bundle, automatically th test mode each of the ten areas of under-rail beams, recording the loop counter running from the reed switch and isolation booth in an emergency increase in the magnetic gap, exploiting the stand and feel under-rail beams zone until they fatigue cracks on the basis of millions of cycles of rolling crane wheels.

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