In this paper, we study the methods for calculating beams with skating in the lower belt of both the I-beam and box sections. Based on the dependences presented in the existing methods, the stress-strain state of single-beam bridge cranes was calculated at the points of contact of the wheels of the hoist and beam belt, with a box section with rolling along the bottom. Box-section crane cranes have greater rigidity and stability compared to the I-beam section, in addition they allow you to increase the span without sacrificing the crane’s lifting capacity. SolidWorks Simulation also performed a finite element analysis of the stress-strain state of box-section beams with skating along the lower belt. The main advantage of the finite element method is the ability to split into finite elements areas of any shape and, thus, the ability to calculate the stress and strain fields in real details, taking into account all their design features, which ensures high accuracy of the calculation. On the basis of the results obtained, the dependences of stresses on the thickness of the lower girder beam, the position of the hoist wheels were studied, an approximating function was constructed, and a simpler engineering calculation method was proposed that allows one to reduce the number of calculations.

The spectrum of probable emergency scenarios for escalators can be analyzed using a computational experiment based on a simulation model that describes the real properties (behavior) of an object in a number of key (reference) States. The reference points of the States of the object under study should be uniquely determined by the complexity of the boundary conditions, for example, by means of measuring tools. The adequately tuned model allows to interpolate intermediate and extrapolate probable States of the studied object. Such approach allows to refuse carrying out full-scale tests with loading of a design to a limiting condition, and thereby to save a resource on bearing capacity of a construction as a whole. Purpose: risk Assessment in the operation of tunnel escalators type ET-2M, equipped with emergency brake with constant torque, without loading the structural elements to the limit state. Methods: vibration Portraiture using vibration measuring complex; modeling of dynamic processes using specialized modules SolidWorks Motion (complex kinematic and dynamic analysis of mechanisms) and SolidWorks Simulation software complex SolidWorks. Results, practical significance: improving the reliability of operation of tunnel escalators equipped with emergency brakes with constant torque by extrapolating the technical condition on the basis of numerical experiment by means of computer aided design.

The article deals with some questions about the influence of drive parameters on the characteristics of hydraulic shock devices, noted during the analysis of the results of mathematical modeling. Using mathematical modeling, numerical experiments were performed and diagrams of the characteristics of a hydraulic shock system were obtained that characterize the dynamics of its operation with various types of drive engines, such as an electric motor, an internal combustion engine, and an «ideal» engine. The parameters of the hydraulic shock device and the setting of the pressure- relive valve remained unchanged. As a result of numerical experiments obtain graphs of displacement and velocity of the piston, displacement of the control valve, pressure in the chambers of working and return stroke, the position of the piston of the accumulator, the pump flow rate in time. A comparison is given of the types of hydraulic shock devices that are currently most widely used in road construction vehicles (equivalent in power to an electric engine and an internal combustion diesel engine). Special attention is paid to the relationship between the parameters of the hydraulic shock device and its drive. The conclusions are made based on the dependencies obtained as a result of computational experiments. The studies show that there are significant influence parameters of the drive on the characteristics of hydraulic impact devices (hammers, breaker), and, accordingly, the need to consider drive parameters by designing and operating it.

The paper contains the results of the probabilistic modelling of joint operation of multidrive belt conveyors in case of their full load as well as without cargo. As a result, modelling demonstrates the need of additional reservation of drive power when designing multidrive belt conveyors. On the basis of the modelling, operational principles of joint operation of belt conveyors are established when there are random slide deviations of their engines. These deviations represent specific conditions of electric motors distribution between the drives as well as the influence features of their parameters on the distribution of the carrying and tractive belts.

The main direction of improving repair processes and current track maintenance, reducing time and labor costs is the maximum mechanization of all track work. A large fleet of track machines and mechanisms is used on domestic highways. However, existing machines do not yet provide for the complete mechanization of all track work. A significant place among such works is the cleaning of railway tracks from weeds (the level of mechanization is 60-65%) and the removal of excess ballast from the middle of the track. The working body of the machines for carrying out these works is a brush pick-up with flexible blades, which ensures that weeds and ballast are cleaned below the level of the rail head without damaging the structural elements of the railway track and turnouts. Due to the sufficient elasticity of the blades, the brush pick-ups do not capture foreign objects in the working area, which protects the transporting elements of the machines from destruction. As a rule, on domestic machines, flexible blades are segments of a steel rope with a diameter of 16-21 mm. The main disadvantage of brush pick-ups is their low efficiency due to the fatigue breaking out of the flexible blades at the exit point. Well-known foreign companies for the manufacture of flexible blades use synthetic materials with internal or external reinforcement. The domestic industry produces a significant range of synthetic materials and products based on them, which makes it promising to increase the efficiency of brush working bodies by manufacturing flexible elements from synthetic materials and optimizing pick-up parameters. This article discusses the results of field tests of the brush pick-up of the KPU-1 machine.

Currently, rubble-cleaning machines with a bar working body for cutting ballast from under the rail-sleeper grid are most widely used on Russian railways. This state of affairs is due to the fact that only machines of this type have the ability to carry out deep cutting of ballast (up to 1 m depth or more), in contrast to previously used machines. The bar working body is the main consumer of power when the machine is operating on a stretch. Structurally, the bar working body of crushed stone cleaning machines is a chain with scrapers with teeth placed on it. The main drive power of the bar chain in this case is naturally spent on cutting the ballast, and, in turn, is determined mainly by the power consumption to overcome the forces arising in the process of interaction of the working body with crushed stone ballast (cutting forces). When determining the cutting force, the formula N.G. Dombrowski, which, however, does not give a completely correct result (as shown by studies conducted at the Russian University of Transport). From the theory of soil cutting it is also known that for cutting perimeters with teeth a more correct result is given by A.N. Zelenin in determining the cutting forces. This can be explained by the fact that the formula A.N. Zelenin takes into account the design features of the cutting organ, in particular the influence of the teeth. The performed calculations showed that the use of the formulas of A.N. Zelenin instead of the formula N.G. Dombrowski in assessing the cutting force of crushed stone ballast is more acceptable when performing design calculations of the power of the cutting device.

One of the actual problems of transport energetic is to meet the requirements for both environmental and technical and economic characteristics of automobile engines. Therefore, to meet these requirements, a new working process for the internal combustion engine was proposed and a new design of the electronically controlled injector was developed in accordance with the requirements of the new working process. One of the essential requirements for the developed design of an electronically controlled injector is high operating speed. Therefore, the objective of this work is the implementation of research to improve the operating speed of the injector. By the method of mathematical modeling investigated the influence of various design parameters on the performance and the operating speed of the injector. The results of the numerical investigations are presented and analyzed. As a result, the rational values of the design parameters of the developed electronically controlled injector are determined.

The article presents a method of computer simulation of the process of time-varying reliability indicators of a key structural element of a mobile ropeway — the rope system as a whole. The method is based on the developed probabilistic mathematical model. At the design stage of the mobile ropeway, it allows predicting the kinetics of reliability indicators during operation of the rope system as a whole, as well as its individual subsystems and structural elements, taking into account the timing and volume of repair and restoration work. She also conduct modeling of the operational stage of the life cycle. The calculation of the probability of finding the rope system in possible combinations of its states at an arbitrary point in time is based on the solution of the Chapman-Kolmogorov linear differential equation system, which is periodically rebuilt at the time moments of scheduled repairs of the mobile ropeway. The results of a test example of calculation in relation to a specific designed mobile ropeway are presented.

The article discusses the development at the design stage of mobile rope complexes of a methodology for the formation of an effective technical and economic strategy for the restoration of critical structural elements of the rope system during scheduled repairs. The technique is based on predicting the kinetics of the probability of failure of the rope system as a whole during its entire life, based on predicting the failure operation of those structural elements of the system whose failure leads to an emergency malfunction of the mobile rope complex. Modeling includes the integration of the Kolmogorov-Chapman system of differential equations, modified due to the need for a discrete change in the probability of failure-free operation of elements to be replaced at the time of scheduled repairs. As a technical and economic criterion for the effectiveness of the rope system recovery strategy, the condition for obtaining the lowest possible total cost of repairs of the rope system throughout the entire period of its operation, while ensuring the average probability of failure-free operation during the entire period of operation was adopted. The formation of this strategy includes planning the schedules, number, time points, volumes and cost of planned repair and restoration measures of the rope system. A description is given of a computer program that implements the developed technique for restoring the operability of a rope system. The results of a test example of calculation in rela

The article presents the results of the development of a force-measuring device for testing auto-coupling devices and absorbing devices of railway vehicles. The technical idea of the device is to physically measure the stresses acting in the characteristic cross sections of the tail of an auto-coupling device, followed by determining the actual force using the developed mathematical model. A calibration schedule of the force measuring device was constructed. The influence of additional bending moments on the measurement accuracy is estimated.

The article deals with the advantages and disadvantages of articulated gear – straight-toothed cylindrical transmission, in which the teeth have convexconcave profiles and interact with each other on the surface. The surface contact of teeth of this transmission provides reduction of contact stresses in gearing in 7-50 times in comparison with involute. It is established that the articulated gear provides a fairly smooth rotation of the driven wheel: the coefficient of unevenness of the stroke is not higher than 0.012. The main disadvantage of this transmission is the radial shocks caused by the oscillation of the center distance. Therefore, gearshifts are recommended for use only at minimum speeds, for example in manual drives.

Traverses are a separate group of General classification of load-grabbing devices used by lifting machines to work with all kinds of goods. Structurally, they represent a linear or spatial (frame) metal structure with various additional elements (branches, grips). Thanks to the traverses, it is possible to eliminate the occurrence of compressive (squeezing) forces of loads, reduce the lifting speed of the hook of the lifting mechanism and reduce the time of the lifting operation. The article presents a brief analysis of existing traverse designs and methods of their calculations. The problem of designing a spatial traverse for use in the painting chamber of a machine-building enterprise is described. A practical example of cargo hanging on a symmetrical traverse is considered as a mandatory element of the technological operation. The necessity of applying the requirements of «safety culture» for all stages of lifting operation is emphasized. The necessity of preliminary preparation of design and operational documentation in connection with the technological features and capabilities of a particular production is indicated. A positive result has been achieved in the implementation of the design of the frame traverse for the painting chamber in conjunction with the safe working methods reflected in the product data sheet and in the operation manual. The conclusions focus on the need to expand the experience to other types and types of traverse, as well as the need for systematization and generalization of the experience, the accumulation of statistical data.

The stability of self-propelled jib cranes is a key task in the process of their operation. The developed calculation scheme of the arrow self-propelled crane and the restrictions imposed on its movement in time and space, allowed to obtain mathematical dependence of the trajectory of the center of gravity of the arrow, a change in the speed of its movement at the arbitrary turn of the arrow, as well as cinematic and energy characteristics of the movement of cargo when combining operations during the operation of the crane. The combination of lifting and lowering cargo and a turn to the unloading place helps to increase productivity during the work of self-propelled jib cranes. Moreover, the full energy of the system (crane structure) depends not only on the position of the center of gravity of the arrow and cargo, but also on the angle of the arrow to the horizon. Moreover, the amount of full energy of the system is directly proportional to the angle of rotation in vertical and horizontal planes. The resulting theoretical dependence studies allow to determine the energy spent on lifting and lowering the load and the trajectory of its movement within the change of the angle of the arrow in the vertical plane.

The article presents the results of simulation and experimental studies of the working processes of transmissions of base stations of mobile cable cars. Mobile cable cars based on special wheeled or tracked chassis are designed for transportation of goods in difficult conditions. Considered the basic scheme of the mobile transmission cable cars. The mathematical model of transmission working processes is presented. The results of modeling with the use of different mathematical models are compared. To confirm the adequacy of the presented mathematical model, experimental studies of transmission reducer of wheeled chassis of high load capacity were performed.

The article presents the results of a study of transmission modes of the GAZon Next medium-duty cargo vehicle. The main goal of the presented scientific work is to obtain empirical data describing the operating modes of the engine and mechanical transmission in operational conditions. Engineers and programmers in the design of the kit, which includes automatic clutch and gearshift control mechanisms, as well as an electronic control unit for them, will use the obtained experimental correlations. Specialists of technical university have developed a measuring system that allows recording in time such parameters as: vehicle speed, acceleration, trajectory, engine operation parameters, loads that occur in the transmission and its drive, as well as the driver’s actions. This article provides a detailed description of the process of preparing vehicle components for research, as well as the installation of a measuring complex. The vehicle was tested at full weight, half of the maximum load and in curb weight to obtain more statistics on the operation of the transmission. In conclusion, the article presents the obtained experimental graphs.

Based on the Navier-Stokes equation, the paper presents the derivation of the tangential flow velocity formula in a hydrocyclone. The derivation coincides with the solution of the vorte3x filament diffusion problem. The formula reflects the influence on the tangential velocity of the geometric and energy parameters of the hydrocyclone. The graphs showing the change in speed along the height of the device are given. A graph of the effect of velocity of the viscosity of the separated medium is given. In a conical hydrocyclone with a vortex circulation ring, the tangential velocity above the ring is increased by adding the velocity component of the vortex ring. At the level of the plane of the ring is reduced considerably, below the plane in this ring it might have the opposite direction, then peripheral sped curves, when approaching the low in the axial part, are significantly increased, taking the additional effect of vortex flow. In a cylindrical hydrocyclone with axial discharge, in with the radial velocities at the wall of the apparatus equal zero, the tangential velocity at the top of the hydrocyclone is almost constant. The increase and surge in velocity is observed only at the lower discharge opening due to the impact of the vortex funnel of the drain. In a flowing cylindrical hydrocyclone near the discharge holes, the radial velocities have different directions, and the tangential velocity near them may also have a reverse direction. To eliminate this phenomenon, the absolute value of the exponential exponent must be used in the tangential velocity formula. If there are several discharge holes, the same tangential velocity near these holes will be equal if the flow through these holes is equal.