Bryansk Automobile Plant

The article provides the analysis of the kinematic scheme version of the end tower positioning mechanism for supporting the driving rope pulley with a carrying-traction rope when placed in the central part of a multi-axle wheeled chassis of high-carrying capacity and cross-country ability. The mechanism enables lifting the end tower from the transport position to the operating position, and its subsequent hydraulic latching in the operating position during the ropeway operation. The article studies the specifics of the main process equipment arrangement on the basic self-propelled chassis. It offers the mathematical models developed for the kinematic and force analysis of the kinematic scheme of the hydraulic mechanism for installing and latching the end tower. The article also presents the analysis of the specified mechanism main structural dimensions impact on the dimensions of the mobile ropeway complex in the transport position, as well as on the force factors occurring in the ropeway operation process. The article defines the conditions for the location and length of the end tower drive hydraulic cylinder required to ensure its positioning and identifies the occurrence of a sizable zone of inadmissible arrangement for the hinged assembly attaching the hydraulic cylinder rod to the end tower metal structure.

The quick-release devices of the ends of the carrying and traction ropes, which have the load capacity required by the tension condition of the rope system and a gentle mechanical effect on the structural elements of steel ropes, make it possible to ensure the rapid deployment and dismantling of mobile ropeways in the conditions of elimination of natural or man-made emergencies. The article discusses the design of the original device that provides a reliable and quick-release connection of the ends of the ropes, and also developed a mathematical model for predicting the load capacity of the specified device. The results of the analysis of the influence of the main design parameters of the connected ropes and fasteners of the device under consideration, as well as the mechanical deformation characteristics of steel ropes on the load capacity of the quick-release device are presented. The calculated dependences for the design of a quick-release device are proposed, taking into account the loading of the rope system during the operation of a mobile ropeway, as well as a methodology for selecting the existing standard size of the connecting device for the specified operating conditions.

During the operation of aerial ropeways, the system of carrying and carrying-traction ropes, which provides the possibility of moving passengers or transported goods between the terminal points of the route, experiences a high level of loading from a variety of operational loads and environmental influences. These loads and influences form the tension of the ropeway system variable along the length of the ropeway route, which has a decisive impact on the main technical and economic indicators of mobile ropeways, and thereby determines specific areas of their effective and inappropriate or unacceptable use. This article presents an engineering technique for constructing tension diagrams of carrying-traction ropes in stationary and non-stationary modes of operation of a mobile ropeway. Calculated dependences are given to determine the tension forces of ropes at characteristic points along their length, as well as calculated dependences for determining the resistance forces to the movement of ropes on characteristic sections of the mobile ropeway route. This technique can be used both for calculating the loading of the rope system based on taking into account a large number of factors characterizing operational loads, terrain parameters and transported cargo, and for analyzing the direction and significance of the variation of these factors and the main design parameters of the main technological equipment of mobile transport and reloading rope complexes. The results of the analysis of the influence of the variation of a number of significant quantitative parameters on the change in the tension forces of the carrying-traction ropes are also presented.

Mobile ropeways for carrying out loading and unloading and transport and transfer operations in previously unsettled or inaccessible areas, formed with the help of terminal base stations connected by a single rope system on the basis of self-propelled wheeled or tracked chassis of increased carrying capacity and cross-country ability, are a promising type of lifting and transport equipment ensuring the prompt deployment of the necessary technological tools. The article deals with the layout of the mechanism for installing and fixing the end tower using a folding bar, consisting of two articulated links. A mathematical model has been developed that provides the required normative vertical dimension of a self-propelled base station of a mobile ropeway with the aim of its safe independent movement to the place of deployment of the ropeway along general roads. The analysis of the influence of standard dimensional requirements, design dimensions of the chassis carrying frame and the height of the end tower on the main design dimensions of the articulated folding rod in the transport position is carried out. Calculations have shown that the considered design makes it possible to provide the standard vertical dimension of a base station on a 6-axle self-propelled chassis with an end tower length of up to 18 m.

The paper presents a dynamic model illustrating the swing of a mobile machine on a wheeled chassis equipped with a loader crane and anchor outriggers during loading and unloading operations. The model regards the interaction effect of the outrigger anchoring device with weak soil within the system “load – loader crane – chassis – outriggers – anchor devices – soil”. Possible variants of single and multiple step soil compaction and changes in its deformation characteristics in the area of the outrigger anchor device implementation are considered. The impact of the gaps formed during soil compaction on the swing parameters of a mobile machine during the swing of the boom of the loader crane is demonstrated as applied to a full-scale crane-manipulator. The rate of chassis tilt angle and swing period of the mobile machine increase during the loader crane operation with an increase in the gaps in the ground. The swing parameters during the initial stage of crane operation gradually increase for soils characterized by multiple compaction until these parameters reach some steady-state values determined by soil stiffness. Awareness of the steady-state value of the crane tilt angle amplitude achieved at the end of the process of weak soil compaction enables to reasonably assess the risk of a mobile machine overturning.