RU206299U1 - SELF-PROPELLED END STATION OF THE MOBILE CABLE - Google Patents

Abstract

The utility model relates to the field of hoisting and transport engineering, namely to devices based on overhead cable car systems for mobile deployment of transport and handling freight and passenger roads in unequipped and hard-to-reach terrain, in the elimination of natural or man-made emergencies. in the form of a mobile chassis equipped with anchor devices, intended for use with another similar chassis as part of a mobile transport and handling rope complex, containing an end support with a rope pulley located on it with drive and tension mechanisms, a mechanism for lifting the end support from the transport position to the operating position with by means of an articulated folding rod, the design of which includes a hydraulic cylinder for moving the hinge of the joint of the upper and lower parts of the folding rod, as well as an enveloping rope pulley moving closed tensioned supporting-hauling rope with towing devices for suspension of transported goods. It differs in that the design of the end support lifting mechanism additionally includes an auxiliary hydraulic cylinder for preliminary lifting of the end support, and in the transport position of the end support, its longitudinal axis and the longitudinal axis of the auxiliary hydraulic cylinder are perpendicular.

Description

The utility model relates to the field of lifting and transport engineering, namely, devices based on overhead rope systems for mobile deployment of transport and handling freight and passenger roads in unequipped and hard-to-reach terrain, in the elimination of natural or man-made emergencies.

The known design of the rear mast for a mobile rope skidding installation (patent RU No. 84181, A01G 23/02, 2009) [1], placed with the possibility of its lateral location on a self-propelled base, having a chassis mounted on it manually driven turntable , moreover, the mast installed on the ground is equipped with vertical and inclined posts connected by means of a hinge, of which the inclined post is attached by means of a trunnion to the turntable, and the vertical post is held by a rope wound on a drum at one end, and the other - packed in blocks on a vertical post for lifting - lowering the mast when it is transferred to the transport position when relocating the mobile rope skidder to a new location.

This design has a number of significant design and functional disadvantages. Firstly, the work on mounting / dismantling the rear mast is not mechanized, it is done manually. Secondly, which is the most important for the proposed utility model, the design of the rear mast does not allow for the movement of the carrying-hauling rope along with the transported load, since the mast only provides tension of the stationary carrying rope for moving carriages-grippers with felled trees along it due to the lack of rotating from the drive mechanism of the rope pulley.

Close in technical essence to the proposed utility model is a self-propelled end station (patent RU No. 200827, В61В 7/00, 2020) [2] in the form of a mobile chassis equipped with outriggers and anchors, intended for use with another similar chassis as part of a mobile a transport and reloading rope complex, containing a drive and tensioning mechanisms, an end support fixed on the overframe structure of the supporting frame, an end support with a rope pulley located on it and an enveloping rope pulley closed tensioned supporting-traction rope with hook-on devices for suspension of transported goods, and the end support with its lower end is hingedly attached to the overframe structure of the bearing frame of the self-propelled end station and has the ability to move in a vertical plane, coinciding with the longitudinal axis of the mobile chassis, at an arbitrary angle of not more than 120 degrees using a lifting hydraulic cylinder, and a rope pulley pivotally attached to the head of the end support is equipped with a khanizm of turning at an angle of no more than 90 degrees with the help of a rotary hydraulic cylinder.

The most significant functional drawback of this design is that to transfer the end support from the transport position to the vertical operating position, it is necessary to use a lifting hydraulic cylinder of significant power and length reaching 3 ... 5 m, and to provide a significant stroke of the hydraulic cylinder rod, corresponding to 80 ... 90% of it length, with the diameter of the hydraulic cylinder up to 250 ... 350 mm [3]. Hydraulic cylinders with such mass-dimensional characteristics are unique and expensive products during their manufacture, and during operation - products with reduced reliability and maintainability characteristics. Another drawback of the considered design is that the end support in the required operating position during the operation of the mobile cable car is held by stopping the piston of the lifting hydraulic cylinder by overlapping the hydraulic lines connecting adjacent cavities of the hydraulic cylinder, and, thus, eliminating the overflow of the working fluid between them under the action of forces on the rod from the side of the operating load. However, due to the finite value of the volumetric elasticity of the real working fluid, the time variability of the operating load, due to the change in the speed of the rope, the weight of the load, its swing under wind action, etc., leads to oscillatory displacements of the piston from the equilibrium position with a small amplitude and the appearance of additional dynamic stresses in the metal structure of the end support, dangerous due to the possible development of fatigue processes in it and the initiation of fatigue cracks in welded seams.

The closest in technical essence to the proposed utility model and adopted for its prototype is the self-propelled end station of the mobile cable car (application RU No.2020141677, В61В 7/00, applied for 12/18/2020, the decision to issue a patent on 03/22/2021) [ 4] in the form of a mobile chassis equipped with anchor devices, intended for use with another similar chassis as part of a mobile transport and handling rope complex, containing an end support with a rope pulley located on it with a drive and tensioning mechanisms, a mechanism for lifting the end support from the transport position to the working position position with the help of an articulated folding rod, the design of which includes a hydraulic cylinder for moving the hinge of the joint of the upper and lower parts of the folding rod, as well as an enveloping rope pulley moving closed tensioned supporting-traction rope with hook-on devices for suspension of transported goods.

The most significant functional drawback of this design is that at the initial moment of lifting the end support from the initial transport position to the required working position close to vertical, the lifting hydraulic cylinder must develop a sufficiently significant tractive effort so that the active lifting torque generated by it relative to the hinge of the end support the support could exceed the total reactive torque from the weight of the metal structure of the end support and both parts of the folding rod, the weight of the rope pulley with the drive and tensioning mechanisms. This is due to the fact that the lifting force acting on the end support, transmitted from the hydraulic cylinder using the upper part of the folding rod, is located at a very acute angle (4 ... 8 degrees) to the longitudinal axis of the end support. Therefore, the traction force created by the hydraulic cylinder must be 7 ... 15 times higher than the required lifting force, which must be applied to the end support to ensure its lifting. With further lifting, the required tractive effort, which should be developed by the lifting hydraulic cylinder, decreases rather quickly, however, nevertheless, design calculations of its mass-dimensional characteristics and power of the hydraulic system pump, strength and dynamic calculations of the supporting metal structure of a self-propelled chassis are performed based on the maximum load, arising during the installation of the end support in the working position.

The technical problem to be solved by the proposed utility model is to reduce the mass-dimensional characteristics of the main lifting hydraulic cylinder and reduce the required power of the hydraulic system pump by installing an auxiliary hydraulic cylinder for preliminary lifting of the end support from the initial transport position, as well as by reducing the load on the supporting frame of a self-propelled mobile the chassis during the installation of the end support in the working position due to a decrease in the maximum force on the rod of the main lifting hydraulic cylinder, which it must develop, and, consequently, a decrease in the magnitude of support reactions and stresses arising in the metal structure of the chassis frame.

To solve the specified technical problem in a self-propelled end station of a mobile cable car in the form of a mobile chassis equipped with anchor devices, intended for use with another similar chassis as part of a mobile transport and handling cable complex containing an end support with a cable pulley located on it with drive and tension mechanisms , a mechanism for lifting the end support from the transport position to the working position with the help of an articulated folding rod, the design of which includes a hydraulic cylinder for moving the hinge of the joint of the upper and lower parts of the folding rod, as well as an enveloping rope pulley moving closed tensioned carrying-traction rope with towing devices for suspension of transported goods, an auxiliary hydraulic cylinder for preliminary lifting of the end support is additionally included in the design of the end support lifting mechanism, and in the transport position of the end support its longitudinal axis b and the longitudinal axis of the auxiliary hydraulic cylinder are perpendicular.

The utility model is explained in more detail using the drawings. All elements not required for direct understanding of the utility model are excluded.

FIG. 1 shows a general view of a self-propelled terminal station with an end support in the transport (non-working) position; Fig. 2 is a general view of a self-propelled end station with an end support in an intermediate position (at the end of the stage of preliminary lifting of the end support); in fig. 3 is a general view of a self-propelled terminal station with an end support in working position; in fig. 4 - section A-A in Fig. 2 (cylindrical hinge for fastening the end support); in fig. 5 - section b-b in Fig. 2 (cylindrical hinge for fastening the body of the main lifting hydraulic cylinder); in fig. 6 - section b-b in fig. 2 (cylindrical hinge for the lower part of the folding rod); in fig. 7 - section Г-Г in Fig. 2 (cylindrical hinge for the upper part of the folding rod); in fig. 8 - section D-D in Fig. 2 (cylindrical hinge for securing the rod of the auxiliary lifting hydraulic cylinder); in fig. 9 - section E-E in Fig. 2 (cylindrical hinge for attaching the housing of the auxiliary lifting cylinder); in fig. 10 is a view A in FIG. 2 (cylindrical hinge for fastening the rod of the lifting hydraulic cylinder and the folding support); in fig. 11 - graphs of changes in the magnitude of the force on the rod of the main and auxiliary lifting hydraulic cylinders for the prototype and the proposed utility model.

The essence of the utility model is as follows.

между центрами шарнирных пальцев 9 (фиг. 1-4) и 42 (фиг. 1-3, 8) и расстояние

между центрами шарнирных пальцев 9 (фиг. 1-4) и 36 (фиг. 1-3,9) должны быть связаны соотношением

где γ_ts - угол наклона продольной оси концевой опоры 5 (фиг. 1-4, 8) в транспортном положении (фиг. 1). На оголовке концевой опоры 5 (фиг. 1-4, 8) установлен канатный шкив 43 (фиг. 1-3), в профилированном пазе которого располагается несуще-тяговый канат 44 (фиг. 2, 3), огибающий канатный шкив 43 (фиг. 1-3). К верхней части концевой опоры 5 (фиг. 1-4, 8) крепится механизм поворота канатного шкива (элемент I на фиг. 1-3). В подшипники качения, использующиеся в конструкции перечисленных цилиндрических шарниров, набита консистентная пластичная смазка, аналогичная рекомендуемой для использования в узлах трения мобильных транспортно-технологических машин [5].On the supporting frame 1 (Fig. 1-3) of the self-propelled end station 2 (Fig. 1-3), an overframe structure 3 (Figs. 1-3, 5, 9) is installed to fix the necessary technological equipment. In the end part of the supporting frame 1 (Fig. 1-3) on the overframe structure 3 (Fig. 1-3, 5, 9), a cylindrical hinge 4 (Fig. 1-3) is fixed, providing a movable (rotary) connection of the overframe structure 3 ( Fig. 1-3, 5, 9) and end support 5 (Fig. 1-4, 8). Cylindrical hinge 4 (Fig. 1-3) is formed by a pair of lugs 6 (Fig. 1-4), fixed, for example, by welding on the overframe structure 3 (Fig. 1-3, 5, 9), and a pair of lugs 7 (Fig. . 4), fixed, for example, by welding on the lower part of the end support 5 (Fig. 1-4, 8). In the coaxial holes of the lugs 6 (Fig. 1-4) and 7 (Fig. 4), equipped with rolling bearings 8 (Fig. 4), a pivot pin 9 (Fig. 1-4) is inserted, providing a movable kinematic connection between the overframe structure 3 (Fig. 1-3, 5, 9) and end support 5 (Fig. 1-4, 8). This design of the attachment point of the end support 5 (Figs. 1-4, 8) allows it to rotate in a vertical plane that coincides with the longitudinal axis of the mobile chassis. To the overframe structure 3 (Figs. 1-3, 5, 9) with the help of a cylindrical hinge 11 (Figs. 1-3) is attached the body of the main lifting hydraulic cylinder 10 (Figs. 1-5). The cylindrical hinge 11 (Fig. 1-3) is formed by a pair of lugs 12 (Fig. 1-3, 5), fixed, for example, by welding on the overframe structure 3 (Fig. 1-3, 5, 9), in coaxial the holes of which the pivot pin 13 is inserted (Figs. 1-3, 5) with the end cap shackle 14 (Fig. 5) of the main lifting hydraulic cylinder 10 (Figs. 1-5) put on it. On the overframe structure 3 (Fig. 1-3, 5, 9) between the cylindrical hinges 4 (Fig. 1-3) and 11 (Fig. 1-3), a cylindrical hinge 15 (Fig. 1-3) is fixed, providing a movable ( pivot) connection of the overframe structure 3 (Figs. 1-3, 5, 9) and the lower part of the folding bar 16 (Figs. 1-3, 6, 10). The cylindrical hinge 15 (Fig. 1-3) is formed by a pair of lugs 17 (Fig. 1-3, 6), fixed, for example, by welding on the overframe structure 3 (Fig. 1-3, 5, 9), and a pair of profiled lugs 18 (Fig. 6) fixed, for example, by welding, on the lower part of the folding bar 16 (Figs. 1-3, 6, 10). In the coaxial holes of the lugs 17 (Fig. 1-3, 6) and 18 (Fig. 6), equipped with rolling bearings 19 (Fig. 6), a pivot pin 20 (Fig. 1-3, 6) is inserted, providing a movable kinematic connection between the overframe structure 3 (Fig. 1-3, 5, 9) and the lower part of the folding bar 16 (Fig. 1-3, 6, 10). This design of the attachment point with the lower part of the folding rod 16 (Figs. 1-3, 6, 10) allows it to rotate in a vertical plane that coincides with the longitudinal axis of the mobile chassis. On the metal structure of the end support 5 (Fig. 1-4, 8), a cylindrical hinge 21 (Fig. 1-3) is fixed, which provides a movable (rotary) connection of the end support 5 (Fig. 1-4, 8) and the upper part of the folding rod 22 (Figs. 1-3, 7, 10). The cylindrical hinge 21 (Fig. 1-3) is formed by a pair of profiled lugs 23 (Fig. 1-3, 7), fixed, for example, by welding on the end support 5 (Fig. 1-4, 8), and a pair of lugs 24 ( Fig. 7), fixed, for example, by welding on the upper part of the folding rod 22 (Fig. 1-3, 7, 10). In the coaxial holes of the lugs 23 (Fig. 1-3, 7) and 24 (Fig. 7), equipped with rolling bearings 25 (Fig. 7), a pivot pin 26 (Fig. 1-3, 7) is inserted, providing a movable kinematic connection between end support 5 (Fig. 1-4, 8) and the upper part of the folding rod 22 (Fig. 1-3, 7, 10). This design of the attachment point for the upper part of the folding rod 22 (Figs. 1-3, 7, 10) allows it to perform plane-parallel movement in the vertical plane coinciding with the longitudinal axis of the mobile chassis. The lower part of the folding rod 16 (Fig. 1-3, 6, 10), the upper part of the folding rod 22 (Fig. 1-3, 7, 10) and the rod 27 (Fig. 1-3, 10) of the main lifting hydraulic cylinder 10 ( Fig. 1-5) are connected by a cylindrical hinge 28 (Fig. 1-3). The cylindrical hinge 28 (Fig. 1-3) is formed by a pair of lugs 29 (Fig. 10) fixed at the end of the lower part of the folding rod 16 (Fig. 1-3, 6, 10), and a pair of lugs 30 (Fig. 10) , fixed at the end of the upper part of the folding rod 22 (Fig. 1-3, 7, 10), into the coaxial holes of which the pivot pin 31 (Fig. 1-3, 10) is inserted with the fastening sleeve 32 put on it (Fig. 10 ) rod 27 (Fig. 1-3, 10) of the lifting hydraulic cylinder 10 (Fig. 1-5). The cylindrical hinge 28 (Figs. 1-3) allows the connected elements to make a mutual pivotal movement relative to the hinge pin 31 (Figs. 1-3, 10) when the rod 27 moves (Figs. 1-3, 10). On the overframe structure 3 (Fig.) Between the cylindrical hinges 4 (Fig. 1-3) and 11 (Fig. 1-3), a cylindrical hinge 33 (Fig. 1-3) is fixed, which provides a movable (rotary) connection of the overframe structure 3 ( Fig. 1-3, 5, 9) and the housing of the auxiliary lifting hydraulic cylinder 34 (Fig. 1-3, 9). The cylindrical hinge 33 (Fig. 1-3) is formed by a pair of lugs 35 (Fig. 1-3, 9), fixed, for example, by welding on the overframe structure 3 (Fig. 1-3, 5, 9), in coaxial the holes of which the pivot pin 36 is inserted (Figs. 1-3, 9) with the shackle of the end cap 37 (Fig. 9) of the auxiliary lifting hydraulic cylinder 34 (Figs. 1-3, 9) put on it. The rod 38 (Fig. 2, 3, 8) of the auxiliary lifting hydraulic cylinder 34 (Fig. 1-3, 9) with the help of a cylindrical hinge 39 (Fig. 1-3) is attached to the end support 5 (Fig. 1-4, 8) ... The cylindrical hinge 39 (Fig. 1-3) is formed by a pair of profiled lugs 40 (Fig. 1-3, 8), fixed, for example, by welding on the end support 5 (Fig. 1-4, 8), and the fastening sleeve 41 ( Fig. 8) of the rod 38 (Figs. 2, 3, 8), in the coaxial holes of which the pivot pin 42 is inserted (Figs. 1-3, 8). The cylindrical hinge 39 (Fig. 1-3) allows the connected elements to make a mutual pivotal movement relative to the hinge pin 42 (Figs. 1-3, 8) when the rod 38 is moved (Figs. 2, 3, 8). In the transport position (Fig. 1) of the self-propelled end station 2 (Figs. 1-3), the longitudinal axes of the end support 5 (Figs. 1-4, 8) and the auxiliary lifting hydraulic cylinder 34 (Figs. 1-3, 9) are perpendicular, t .e. the angle α (Fig. 1) is 90 degrees. To ensure this, the following condition must be met when designing: distance

between the centers of the hinge pins 9 (Fig. 1-4) and 42 (Fig. 1-3, 8) and the distance

between the centers of the hinge pins 9 (Fig. 1-4) and 36 (Fig. 1-3.9) should be connected by the ratio

where γ _ts is the angle of inclination of the longitudinal axis of the end support 5 (Fig. 1-4, 8) in the transport position (Fig. 1). On the tip of the end support 5 (Fig. 1-4, 8) there is a rope pulley 43 (Fig. 1-3), in the profiled groove of which there is a supporting-traction rope 44 (Fig. 2, 3), a bending rope pulley 43 (Fig. . 1-3). To the upper part of the end support 5 (Figs. 1-4, 8) is attached a mechanism for turning the rope pulley (element I in Figs. 1-3). The rolling bearings used in the design of the listed cylindrical hinges are packed with a grease similar to that recommended for use in friction units of mobile transport and technological machines [5].

The utility model works as follows.

To the destination, the self-propelled end station 2 (Fig. 1-3) is extended, having the end support 5 (Fig. 1-4, 8) in the transport position (as shown in Fig. 1). In order to prevent breakages of the metal structure of the end support 5 (Fig. 1-4, 8) due to movement on an uneven surface, in the transport position, the end support 5 (Fig. 1-4, 8) rests and is fixed on the transport rack 45 (Fig. 1- 3). Upon reaching the destination, the self-propelled end station 2 (Figs. 1-3) is oriented in such a way that the longitudinal axis of the mobile chassis coincides with the longitudinal axis of the cable car. To ensure overall stability under conditions of significant horizontal overturning loads from the tension force of the supporting-traction rope 44 (Fig. 2, 3) and the weight of the transported cargo, the self-propelled end station 2 (Fig. 1-3) is installed on outriggers 46 (Fig. 1 -3), which are fixed to the ground by means of anchoring devices 47 (Fig. 2, 3). As anchor devices 47 (Fig. 2, 3) can be used known anchor structures [6]). The lifting of the end support 5 (Figs. 1-4, 8) is performed in two stages. During the first stage - the stage of preliminary lifting - the end support 5 (Fig. 1-4, 8) is lifted from the initial transport position (Fig. 1) to an intermediate position (Fig. 2). The transfer of the end support 5 (Figs. 1-4, 8) to an intermediate position is performed by an auxiliary lifting hydraulic cylinder 34 (Figs. 1-3, 9) by extending the rod 38 (Figs. 2, 3, 8). To do this, through pressure pipelines (conventionally not shown) using a volumetric hydraulic pump (conventionally not shown), the working fluid is supplied under pressure from the hydraulic system of the self-propelled end station 2 (Figs. 1-3). In this case, the main lifting hydraulic cylinder 10 (Fig. 1-5) is disconnected from the hydraulic system of the self-propelled end station 2 (Fig. 1-3), as a result of which its rod 27 (Fig. 1-3, 10), the cylindrical hinge 28 (Fig. 1 -3) and both parts of the folding bar 16 (Fig. 1-3, 6, 10) and 22 (Fig. 1-3, 7, 10) move freely following the movement (rotation) of the end support 5 (Fig. 1-4 , 8), with which they are kinematically connected by means of a cylindrical hinge 21 (Figs. 1-3). The extension of the rod 38 (Fig. 2, 3, 8) ends when the required pre-inclination angle γ _ps (Fig. 2) of the end support 5 (Fig. 1-4, 8) and the auxiliary lifting hydraulic cylinder 34 (Fig. 1-3, 9) is disconnected from the hydraulic system of the self-propelled end station 2 (Fig. 1-3) by blocking the pressure pipeline (conventionally not shown) supplying the working fluid to it under pressure. The working fluid located in the hermetically sealed housing of the auxiliary lifting hydraulic cylinder 34 (Figs. 1-3, 9), due to its inherent incompressibility, does not allow the end support 5 (Figs. 1-4, 8) to go down under its own weight. The maximum stroke of the rod 38 (Fig. 2, 3, 8) of the auxiliary lifting hydraulic cylinder 34 (Fig. 1-3, 9) is limited by its length, therefore, in the space under the end support 5 (Fig. 1-4, 8) in the transport position it is possible to place an auxiliary lifting hydraulic cylinder 34 (Figs. 1-3, 9) of a sufficiently limited length, as a result of which the angle of preliminary inclination is γ _ps ~ (1 ... 2) γ _ts , i.e. _{turns out to be much less than the angle γ ws} required for the installation of the end support 5 (Figs. 1-4, 8) in the working position (Fig. 3). Therefore, further lifting of the end support 5 (Fig. 1-4, 8) requires the mandatory use of the main lifting hydraulic cylinder 10 (Fig. 1-5). Before the start of the second stage - the stage of the final lifting of the end support 5 (Fig. 1-4, 8) into the working position (Fig. 3) - the crown nut 48 (Fig. 8) and the pivot pin 42 (Fig. 1-3, 8 ) is removed from the cylindrical hinge 39 (Fig. 1-3), thereby the rod 38 (Fig. 2, 3, 8) of the auxiliary lifting hydraulic cylinder 34 (Fig. 1-3, 9) is disconnected from the end support 5 (Fig. 1- 4, 8). In such an inclined position, the auxiliary lifting hydraulic cylinder 34 (Figs. 1-3, 9) is held by means of a retaining rod 49 (Figs. 1-3), one end of which is pivotally connected to a collar 50 (Figs. 1-3), fixed on the body of the auxiliary lifting hydraulic cylinder 34 (Fig. 1-3, 9), and the second one is hingedly fixed by means of the lug 51 (Fig. 1-3) on the overframe structure 3 (Fig.) of the self-propelled end station 2 (Fig. 1-3) ... The end support 5 (Fig. 1-4, 8) is transferred to the working position by the main lifting hydraulic cylinder 10 (Fig. 1-5) by pulling the rod 27 (Fig. 1-3, 10) inside its body. To do this, through pressure pipelines (conventionally not shown) using a volumetric hydraulic pump (conventionally not shown), the working fluid is supplied under pressure from the hydraulic system of the self-propelled end station 2 (Figs. 1-3). The rod 27 (Fig. 1-3, 10) moves the cylindrical hinge 28 (Fig. 1-3) towards the cabin 52 (Fig.) Of the self-propelled end station 2 (Fig. 1-3) in the longitudinal vertical plane, and it makes complex plane-parallel movement - translational along the longitudinal axis of the main lifting hydraulic cylinder 10 (Fig. 1-5) and rotary relative to the pivot pin 20 (Fig. 1-3, 6). This increases the angle β (Fig. 2) of crossing the longitudinal axes of the lower 16 (Fig. 1-3, 6, 10) and upper 22 (Fig. 1-3, 7, 10) parts of the folding bar. The lower part of the folding rod 16 (Fig. 1-3, 6, 10) acts on the upper part of the folding rod 22 (Fig. 1-3, 7, 10), forcing it to move upward, while simultaneously turning relative to the hinge pin 31 (Fig. 1 -3, 10) of the cylindrical hinge 28 (Fig. 1-3) in the longitudinal vertical plane in the opposite direction from the cab 52 (Fig.) Of the self-propelled end station 2 (Fig. 1-3). In turn, the upper part of the folding rod 22 (Fig. 1-3, 7, 10) acts on the end support 5 (Fig. 1-4, 8) at the point of attachment of the cylindrical hinge 21 (Fig. 1-3), forcing the support pivot in the longitudinal vertical plane relative to the cylindrical hinge 4 (Fig. 1-3) and, thus, rise to the required working position (Fig. 3). The working position of the end support 5 (Fig. 1-4, 8) is achieved when the longitudinal axes of both parts of the folding rod 16 (Fig. 1-3, 6, 10) and 22 (Fig. 1-3, 7, 10) are combined ( i.e. when the angle β becomes equal to 180 °). At this moment, the movement of the rod 27 (Figs. 1-3, 10) stops due to the actuation of the limit switch (conventionally not shown) installed on the stop plate 53 (Figs. 1, 2, 10). Actuation of the limit switch leads to the shutdown of the volumetric hydraulic pump (conventionally not shown) of the hydraulic system of the self-propelled end station 2 (Fig. 1-3) and, thus, to stop the rod 27 (Fig. 1-3, 10) of the main lifting hydraulic cylinder 10 (Fig. 1 -5). During the operation of the mobile cable car, the hydraulic line is opened (conventionally not shown) between the adjacent cavities of the main lifting hydraulic cylinder 10 (Figs. 1-5), which leads to equalization of the working fluid pressure in them and the elimination of additional dynamic stresses during the operation of the mobile cable car. The entire operating load is taken by the folding rod, which operates under tension and ensures that the end support 5 (Figs. 1-4, 8) is held in the required operating position. Upon completion of the work of the mobile cable car, the transfer of the end support 5 (Figs. 1-4, 8) from the working position to the transport position is carried out in the reverse order in two stages. First, the rod 27 (Fig. 1-3, 10) of the main lifting hydraulic cylinder 10 (Fig. 1-5), to which the working fluid is supplied from the hydraulic system of the self-propelled end station 2 (Fig. 1-3), makes a reverse movement until until the end support 5 (Fig. 1-4, 8) reaches an intermediate position (Fig. 2) with an angle of inclination γ _ps . An articulated pin 42 (Fig. 1-3, 8), forming a cylindrical hinge 39 (Fig. 1-3), and is fixed with a castellated nut 48 (Fig. 8). Next, the working fluid from the hydraulic system of the self-propelled end station 2 (Fig. 1-3) is fed into the auxiliary lifting hydraulic cylinder 34 (Fig. 1-3, 9), the rod 38 (Fig. 2, 3, 8) of which makes a return motion until until the end support returns to its original transport position (Fig. 1) with an inclination angle γ _ts . In this position, it is attached to the transport rack 45 (Figs. 1-3).

отношение мощности насосов

отношение максимальных значений опорных реакций в цилиндрических шарнирах крепления концевой опоры, основного подъемного гидроцилиндра и нижней части складывающейся штанги

отношение максимальных значений напряжений в металлоконструкции

Для рассмотренного на фиг. 11 конкретного варианта исполнения

Таким образом, для предлагаемой полезной модели диаметр основного гидроцилиндра оказывается меньше приблизительно в 1,8 раза, мощность насоса гидросистемы, максимальные значения опорных реакций и максимальные действующие напряжения в металлоконструкции - в 3,4 раза. Эти оценочные расчеты подтверждают наличие технико-экономического результата от использования предлагаемой полезной модели.The technical and economic result from the introduction of the utility model is achieved by reducing the mass and dimensional characteristics of the main lifting hydraulic cylinder, which needs to overcome significantly lower loads when lifting the end support from the transport position to the working position, as well as by reducing the load on the metal structure of the self-propelled end station supporting frame in connection with a significant decrease in support reactions in the places where the main lifting hydraulic cylinder and end support are attached to it. FIG. 11 shows the graphs of changes in the amount of force on the rod of the lifting hydraulic cylinder for the prototype as the end support rises (graph 1), as well as on the rods of the main and auxiliary lifting hydraulic cylinders for the proposed utility model (graph 2) using the example of an end support 10 m long installed on a four-axle wheeled chassis [3]. As applied to the prototype (graph 1 in Fig. 11), large values of the force on the rod of the lifting hydraulic cylinder in the initial period of lifting from the transport position are due to the fact that the lifting force acting on the end support transmitted by the upper part of the crossing rod acts at a very acute angle (5 ... 10 deg) to the longitudinal axis of the end support. Therefore, in order to create the necessary torque relative to the hinge of the end support attachment to the overframe structure, the lifting hydraulic cylinder must create a significant force on the rod. As the end support rises (with an increase in the angle γ _t ), the angle between the longitudinal axes of the end support and the upper part of the crossing rod increases and, accordingly, the force required to lift the end support on the hydraulic cylinder rod monotonically decreases. With regard to the proposed utility model (graph 2 in Fig. 11), at the initial stage - the stage of preliminary lifting of the end support - in the range of angles γ _ts ≤ _{γ t} ≤ γ _{ps, the} lifting force is created by an auxiliary lifting hydraulic cylinder, which has an optimal rod location in transport state: its longitudinal axis is perpendicular to the longitudinal axis of the end support. Therefore, the force R _{hc, n. Model is} significantly less than the force R _hc , _prototype . At the second stage - the stage of the final lifting of the end support - the lifting force, as in the prototype, is created by the main lifting hydraulic cylinder, therefore, in the range of angles γ _ps ≤ _{γ t} ≤ γ _ws forces R _{hc, n} . Model = R _hc , _prototype . The jump in graph 2 is associated with the transition from the operation of the auxiliary hydraulic cylinder to the operation of the main hydraulic cylinder. Technical characteristics such as weight and size parameters of hydraulic cylinders, pump power of the hydraulic system of a self-propelled end station, support reactions and the associated stresses in the metal structures of the end support, the overframe structure and the supporting frame are determined by the maximum values of the forces on the hydraulic cylinder rod, which must be created when lifting the end supports from transport position to working position. So, the ratio of the diameters of the lifting hydraulic cylinders

pump power ratio

the ratio of the maximum values of support reactions in the cylindrical hinges of the end support attachment, the main lifting hydraulic cylinder and the lower part of the folding rod

the ratio of the maximum stress values in the metal structure

For the one discussed in FIG. 11 specific version

Thus, for the proposed utility model, the diameter of the main hydraulic cylinder turns out to be approximately 1.8 times less, the power of the hydraulic system pump, the maximum values of the support reactions and the maximum acting stresses in the metal structure - 3.4 times. These estimated calculations confirm the existence of a technical and economic result from the use of the proposed utility model.

Sources of information

1. Pat. 84181 Russian Federation, IPC A01G 23/02. Rear mast for mobile rope skidding / Grigoriev I.V., Zhukova A.I., Ivanov A.V., Grigorieva O.I., Kiselev D.S. - No. 2009107586/22; app. 03/04/2009; publ. 10.07.2009, Bul. No. 19.

2. Pat. 200827 Russian Federation, IPC В61В 7/06. Self-propelled end station / Lagerev A.V., Lagerev I.A., Tarichko V.I .; applicant and patentee FBGOU VO “Bryansk State University named after Academician I.G. Petrovsky ". - No.2020117118; app. 05/12/2020; publ. 12.11.2020, Bul. No. 32.

3. Lagerev A.V., Tarichko V.I., Lagerev I.A. Arrangement of technological equipment on the base chassis of a mobile transport and reloading rope complex // Scientific and technical bulletin of the Bryansk State University. 2020. No. 3. S. 388-403. DOI: 10.22281 / 2413-9920-2020-06-03-388-403.

4. Application 2020141677, IPC В61 В 7/06. Self-propelled end station of the mobile cable car / Lagerev A.V., Lagerev I.A., Tarichko V.I .; applicant FBGOU VO “Bryansk State University named after Academician I.G. Petrovsky ". Appl. 16.12.2020. Decision to issue a patent on 03/22/2021.

5. Ivashkov I.I. Installation, operation and repair of hoisting-and-transport machines. M .: Mashinostroenie, 1981.335 p.

6. Lagerev I.A., Lagerev A.V. Modern theory of manipulation systems of mobile multipurpose transport and technological machines and complexes. Design and operating conditions. Bryansk: RIO BSU, 2018.190 p.

Legend of positions on figures

Claims (1)

Self-propelled end station of a mobile cable car in the form of a mobile chassis equipped with anchor devices, intended for use with another similar chassis as part of a mobile transport and handling rope complex, containing an end support with a rope pulley located on it with drive and tension mechanisms, a mechanism for lifting the end support from transport position into the working position with the help of an articulated folding rod, the design of which includes a hydraulic cylinder for moving the hinge of the joint of the upper and lower parts of the folding rod, as well as an enveloping rope pulley moving closed tensioned supporting-traction rope with towing devices for suspension of transported goods, which differs by the fact that an auxiliary hydraulic cylinder for preliminary lifting of the end support is additionally included in the design of the end support lifting mechanism, and in the transport position of the end support its longitudinal axis and the longitudinal axis in auxiliary cylinders are perpendicular.

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