Parameter Calibration and System Design of Material Lifting System for Inclined Shaft Construction

Abstract

As a key transportation equipment in the construction of long tunnels with large slope, the material hoisting system plays an important role in the transportation of materials in sloping shafts. This paper proposes a parameterized calibration scheme for the hoisting system based on the structure and working principle of the hoisting system, taking the wire rope, hoist, motor and overhead wheel as the research objects, and according to the relevant industry specifications and numerical calculation methods. Based on the structural design and functional analysis of the hoisting system, a reasonable control system, monitoring system and safety protection devices are designed, and the calibration scheme and the designed system are introduced into the Dianzhong water diversion project for verification. The parameters of each component of the hoisting system were calculated as follows: maximum breaking tension value of wire rope 490.29 KN, drum diameter 2000 mm, motor hoisting power 213.7 KW, and the system design was as follows: control system selects frequency conversion electric control method, safety protection device selects ZDC30-2.5 anti-running device. The results show that: the hoisting system components structure parameters meet the specification requirements—safety protection devices can effectively prevent the occurrence of sports car slippage and man-car jumping rail overturning accident—to meet the requirements of the construction period transport capacity and transport safety. The relevant experience can provide the basis for the design of a material hoisting system for a similar inclined shaft construction.

1. Introduction

The ramp hoisting system is the key equipment for material transportation in large slope tunnel construction, and its safe and reliable operation directly affects the productivity of construction companies and the safety of personnel and property on site [1,2]. The ramp hoisting system is mainly used for the transportation of materials, cavern slag, utensils, personnel and concrete during excavation support and concrete and grouting construction [3,4,5], and the design must meet the requirements of transportation capacity and transportation safety during construction.

At present, there are more abundant studies on inclined shaft hoisting systems at home and abroad [6,7]. In the application of slant shaft hoisting system design, Li et al. [8] used the method of scheme comparison to select the optimal hoisting system transportation scheme for the Dianchi water replenishment Dawushan tunnel project. Yang et al. [9] compared and analyzed the mine hoisting system from three aspects of arrangement, parameter selection and component selection, and selected a reasonable mine main inclined shaft hoisting scheme. Lukichev et al. [10] used a vertical blind bucket hoisting shaft with conveyor excavation and transportation for mineral mining operations, and the results showed that the system could effectively improve the mine transportation capacity and transportation efficiency. Calver et al. [11] discussed the practicality of two inclined shaft transportation systems in practical engineering, and experimentally verified the causes and solutions of rope slackness during the operation of the hoisting system. Popescu et al. [12] devised a model for calculating the braking temperature of a mine car of hoisting system, through which the temperature of the track surface material can be effectively calculated to ensure the safety of the mine car operation. Qiu et al. [13] manufactured a two-inclined section mine transportation system through parameter selection design, and the results showed that the system parameters meet the design specification requirements and can ensure the safe transportation of construction personnel and materials. Zhou et al. [14] found that for large section tunnel projects, the tunnel hoisting system incorporating roof deflection control technology can effectively guarantee the safety of construction materials and personnel transportation.

With the continuous development of hoisting technology, hoisting system equipment modification and fault detection have also gradually received attention [15]. In terms of system equipment modification, Li et al. [16] showed that the permanent magnetic hoist has greater advantages and broad application prospects in energy saving compared with ordinary hoists by verifying the performance of the hoist. Pei et al. [17] relied on the Xinda coal mine project and obtained that adding a new hoist next to the existing hoist is beneficial to the safe operation of the hoisting system. Yan et al. [18] researched an automatic monitoring and data transmission system, which is based on the limit state assessment theory and can visually evaluate the equipment vibration status of the slope hoisting system. In terms of fault detection, Ince et al. [19] used a neural net to detect hoist motor faults and extracted the features of the faults into a single learning body, proving the effectiveness of the scheme for real-time hoist fault monitoring. Olszyna et al. [20] used a laser to measure the dimensional parameters of the groove formed by the wire rope on the drum to determine the safety condition of the rope system and thus take partial corrective measures to ensure that the rope system works safely. Zhang et al. [21] proposed a safety monitoring system for real-time monitoring of mine hoisting systems. By monitoring various indicators such as equipment brake valve, oil pressure and operating speed, the operating status of the mine hoisting system is judged in real time. In summary, most scholars have studied the slope hoisting system through two perspectives of system equipment modification and fault detection but have not started the research from the detailed calculation and design of the parameters of each component of the hoisting system and the optimization design of each auxiliary system.

Based on this, this paper proposes a parameterized calibration scheme for the hoisting system from the perspective of the structure and working principle of the hoisting system, determines the structural parameters of the hoisting system components, designs the control system selection scheme, and finally verifies the application in the Dianzhong water diversion project. The research results can provide new ideas for the design of related hoisting systems.

2. Lifting System Parameter Calibration Method

Combining the lifting system composition structure, working principle and factors such as materials and equipment transported during the tunnel construction, a parametric calibration selection scheme for the lifting system is proposed, and the specific process is as follows:

2.1. Wire Rope Parameters Calibration

According to the Safety Requirements for Mine Hoists and Mine Hoisting Winches (GB20181-2006) [22], the wire rope safety factor $m$ should be greater than 6.5 when the hoisting system is used to lift materials. Wire rope safety factor $m$ as in Equation (1):

$$m=\frac{Q_q}{\left[(G+G_0)(\sin \theta +\omega \cos \theta )+q{L}_c(\sin \theta +{\omega }^{\text{'}}\cos \theta )\right]g}>6.5$$

(1)

where $Q_q$ is the sum of wire rope breaking tension (KN); $q$ is the wire rope per meter mass (kg/m); $\theta$ is the lifting tilt angle (°); $G$ is the concrete truck in the lifting cargo mass (kg); $G_0$ is the concrete truck mass (kg); $\omega$ is the skip running resistance coefficient, generally can be used = 0.01~0.015; ${\omega }^{\text{'}}$ is the wire rope running resistance coefficient, generally can be used = 0.15~0.2; $g$ is the gravity acceleration, take 9.8 m/s², $L_c$ is the length of the wire rope (m).

Hoist wire rope maximum static tension $F_j$ such as Formulas (2) and (3):

$$Q_s=Q_q(\sin {22}^{\circ }+\omega \cos {22}^{\circ })$$

(2)

$$F_j=Q_{s}g$$

(3)

where $Q_s$ is the wire rope end load (KN).

2.2. Drum Parameters Calibration

According to Safety Requirements for Mine Hoists and Mine Hoisting Winches (GB20181-2006), the ratio of hoisting system drum diameter and wire rope diameter should be greater than 60. The number of layers of wire rope winding on the drum according to the following provisions: when the hoisting system to lift personnel or materials, winding layer for 2 layers; when dedicated to lifting materials, winding layer for 3 layers. The design of this paper is dedicated to lifting materials, so it takes 3 layers.

Therefore, the drum diameter $D$ is as in Equation (4):

$$D\ge Md$$

(4)

where $d$ is the wire rope diameter (mm); $M$ is the scale factor, 60.

The width of the roller $B$ is calculated as in Equations (5) and (6):

$$D_p＝D+\frac{k-1}{2}\sqrt{4d^2-{(d+\epsilon )}^2}$$

(5)

$$B=\frac{H+30+(n^{\text{'}}+3)\pi D}{k\pi D_p}(d+\epsilon )$$

(6)

where $D_p$ is the average winding radius of wire rope (mm); $k$ is the number of winding layers, 3; $H$ is the lifting height (m); $n^{\text{'}}$ is the number of wrong rope circle; $\epsilon$ is the wire rope circle gap (mm).

Physical diagram of steel wire rope and drum is shown in Figure 1.

2.3. Motor Parameter Calibration

According to the Safety Requirements for Mine Hoists and Mine Hoisting Winches (GB20181-2006), the maximum speed of the hoisting system should be no more than 5 m/s when the mine car is used to hoist the materials, and no more than 7 m/s when the skip is used to hoist the materials. Therefore, the hoist speed is in principle calibrated according to the maximum speed of no more than 5 m/s. For the convenience of calculation, the motor type is determined as a permanent magnet synchronous motor.

The maximum speed $V_m$ is as in Equation (7):

$$V_m=\frac{\pi Dr}{60i}$$

(7)

where $i$ is the reduction ratio; $r$ is the motor speed ($r/\min$).

Motor power $N$ as in Equation (8):

$$N=\frac{K{F}_j{V}_m}{1000\eta }$$

(8)

where $K$ is the motor power spare factor; $\eta$ is the motor drive efficiency.

The permissible input power $PC$ of the motor reducer is as in Equation (9):

$$PC=P\times R\times S$$

(9)

where $P$ is the motor power (KW); $R$ is the working condition factor, take 1.5~2; $S$ is the safety factor, take 1.5~2.

The physical diagram of the hoisting system motor is shown in Figure 2.

2.4. Skywheel Parameter Calibration

According to the Safety Requirements for Mine Hoists and Mine Hoisting Winches (GB20181-2006): (1) For the shaft hoist, the ratio of the diameter of the hoist to the diameter of the wire rope should be greater than 60 when the envelope angle of the hoist is less than 90°; (2) The hoist wire rope should be lower than the edge of the hoist when it passes through the hoist, and the distance between them should be greater than 1.5 times of the diameter of the wire rope. Therefore, the diameter of the skywheel $D_t$ and the depth of the wheel groove $h$ are as follows as in Equations (10) and (11):

$$D_t\ge 60d$$

(10)

$$h=2.5d$$

(11)

The physical diagram of the hoisting system overhead wheel is shown in Figure 3.

3. System Design

3.1. Control System Design

According to the Safety Requirements for Mine Hoists and Mine Hoisting Winches (GB20181-2006), the electromechanical control system of hoisting devices shall conform to the following provisions:

(1)

The main control system can maintain a stable working condition and accurately calculate the operating parameters and position of the mine car, and can balance the main operating parameters, such as the operating speed of the mine car, the operating temperature of the hoist, the operating speed of the motor and other equipment working parameters, so as to avoid the safety risks caused by uncontrolled work.

(2)

The main control system must be able to accurately control all the operating parameters of the hoist, including mine car speed, motor current, hoist hook number, motor speed and other parameters to ensure the safety and efficiency of the hoist system at work.

(3)

The main control system must have a high degree of safety and reliability to ensure the safe operation of the equipment in the process of mine car hoisting. When the equipment parameters exceed the safety threshold, the main control system can send a signal to remind the operator in time and automatically perform safe braking operation.

(4)

The main control system should be able to adapt to the complex construction environment and ensure the flexibility of the work of the main control system through continuous debugging in different working environments.

(5)

The main control system should be simple and reliable, with a high degree of safety. The operator should follow the operation specification when manipulating the system and develop the corresponding operation procedure according to the safety regulations.

(6)

The main control system should provide the operator with a simple and easy to understand display interface and easy to understand operating functions, so that the operator’s eyes do not need to explore too much and can achieve simple control operations.

At present, there are mainly three design schemes of common electric control, dual PLC and frequency electric control for inclined shaft hoisting control systems, and their main performance is compared as follows:

• Ordinary electric control system

Main configuration: Stator screen, rotor screen, relay screen, etc.

Working principle: Connect the resistor in the rotor of the hoist and use the control equipment to adjust the speed by slowly dividing the resistor. The advantage of the ordinary electronic control system is that the cost is small and the system is simple and easy to maintain; the disadvantage is that the system operates on the loss of resources and poor regulation performance.

2.

PLC electronic control system

Main configuration: Power commutation cabinet, operation desk, sub-PLC console, speed generator, etc.

Working principle: Using two PLC systems with mixed control, through the digital module to receive and output high-speed pulse signal, can accurately calculate the specific position and operating status of the slope mine car, digital, information technology, etc. to provide safety protection, speed control and other functions for the slope hoisting system. The advantages of PLC electronic control system is safe and reliable equipment, small size, low energy consumption and strong versatility. The disadvantages are that the costs are high and the technology is relatively complicated.

3.

Variable frequency electric control system

Main configuration: Operation desk, high-voltage switchgear, PLC control cabinet, etc.

Working principle: Using frequency conversion technology to convert the industrial frequency power supply to AC power supply and change the running state of the motor by adjusting the stator frequency. The advantages are good energy saving, high control precision and stable working condition. The disadvantage is that the high harmonics of the inverter output has a certain negative impact on the motor operation.

The PLC cabinet of the control system and the physical diagram of the operation table are shown in Figure 4.

3.2. Monitoring System Design

In order to ensure that operators can monitor the operating parameters of the hoisting system and the operating status of the mine car in real time during the operation of the hoisting system, a real-time monitoring system of the inclined shaft hoisting system is designed. The monitoring system consists of two parts: data center and monitoring equipment. The data center includes terminal monitoring system components such as optical terminal, video matrix, head and head decoder embedded in the main control system, and the monitoring equipment includes front-end monitoring equipment such as motor current monitor, mine car speed monitor and mine car driving distance monitor installed in the inclined shaft mine car. The display interface of the monitoring system is shown in Figure 5.

Through the hoist monitoring system, the operator can realize the following operation functions:

(1)

The dynamic and static screen generation of the hoisting system, such as the dynamic display of the mine car hoisting process, dynamic display of speed curve, dynamic display of armature current curve, dynamic display of hoisting vessel position, etc.

(2)

The fault self-test and self-inspection of the hoisting system, and can alarm the operator in time through the display interface of the monitoring system. The monitoring system can display the location, time and cause of the fault; monitor the important parameters of the system such as speed, current, voltage and operation status in real time; and store and process the important parameters such as speed graph and armature graph.

(3)

The monitoring system can monitor the power supply of each circuit of the hoisting system and realize real-time control of the speed of the speed control system by cooperating with the main control system to complete the operation of the hoist as fully automatic, semi-automatic, manual, maintenance, slow moving, emergency stop, low speed crawling, etc.

(4)

The data center of the monitoring system adopts modularized function and linearized structure design, which has good maintainability and expandability. The speed regulation and monitoring at the slope construction site can realize the ability of remote real-time control and diagnosis, which can assist users to analyze the operation status of the hoist in time and make corresponding adjustments.

3.3. Safety Protection Device Design

3.3.1. Sports Car Guards

In order to ensure the safe operation of the inclined shaft hoisting system, the hoisting system should be set up with runaway protection devices. The running car protection device should include a car stopper and car blocking bar. According to the Coal Mine Safety Regulations, the car stopper is arranged in the following way: (1) at the entrance of the yard, the car stopper that can stop the vehicle from driving in time; (2) at the location of the change of slope in the yard, the car stopper that can stop the vehicle from sliding into the inclined shaft. According to the Safety Regulations for Metal and Non-metal Mines (GB16423-2020 [23]), the upper part of the inclined shaft and the middle section of the yard must be set up with a certain number of stop bars and car stoppers. The following are the calculations of the maximum distance of the installation of the anti-cars device and the advance amount of the opening of the blocking bar.

The anti-running device installation of the maximum distance $L_{\max }$ is as in Formula (12):

$$L_{\max }=(E-\frac{1}{2}m{v}_0^2)/(mg(\sin \alpha -\mu \cos \alpha ))$$

(12)

where $E$ is the blocking bar impact energy (J); $m$ is the total mass of transported material (kg); $v_0$ is the initial speed of the lifting system (m/s); $\mu$ is the operating resistance coefficient of the lifting system; $\alpha$ is the inclination angle of the inclined shaft track (°).

The advance for opening the barrier $L_{\min }$ is as in Equation (13):

$$L_{\min }=v\frac{H}{v^{\text{'}}}$$

(13)

where $v$ is the maximum speed of winch operation (m/s); $H$ is the lifting height (m); $v^{\text{'}}$ is the blocking bar running speed (m/s).

3.3.2. Mine Car Holding Rail Braking Device

In order to further increase the safety of the inclined mine car in the transport of construction materials, when there is wire rope breakage and hoist equipment failure, the inclined mine car can be timely braking and does not occur in the inclined shaft jump rail overturning accident, resulting in property damage or personal safety accidents, there is an inclined mine car chassis installed holding rail brake device. The device structure diagram in Figure 6.

In Figure 6, when the mine car is running normally, the opening spring is always in a compressed state under the tension of the wire rope, and the tie rod is connected to the wire rope through a series of connecting devices. When there is an abnormal situation leading to the occurrence of a sports car accident, the hoist wire rope slackens, then the spring opens under pressure because the external force disappears and restores to the original state. Its elongation drives the block fixed on the tie rod with backward movement. When the tie rod drives the block with backward movement, the upper part of the tie rod iron will also slide backward. In the process of sliding, the iron collision jaws make the jaws rotate, which then leads to the separation of the jaws and the support block. The brake springs because the squeeze pressure disappears and restores to the original state. This drives the guide rod with forward movement, driven by the guide rod, held down to hold the lower track, which completes the procedure to the rail to stop the mine car. Its brake after the photo is shown in Figure 7.

4. Case Study

4.1. Project Overview

The Yunnan Central Water Diversion Project is the largest water diversion project under construction in China, with a total length of 755.44 km for all kinds of buildings. Among them, the total length of the dry canal of Kunming section construction 5 is 20.97 km. Seven construction branch tunnels are included in this section, which are the Kuncheng Tunnels #1–#7 construction branch tunnels. Among them, the characteristics of the #1 construction branch tunnel are shown in

Table 1. Construction support hole characteristics.

Parameter Name	Inclined Shaft Construction Support Hole
Intersection pile number with the main cave	KCT3 + 040.637
Inlet base plate elevation (m)	2512.500
Cross main cave floor elevation (m)	1892.388
Height difference (m)	620
Maximum Inclination (°)	22°
Length/m	1655.265

.

According to the arrangement of the overall construction procedure, Kuncheng #1 construction branch cave mainly undertakes the construction task of its main cave KT1 + 0~KCT4 + 263.811 section of about 3263.811 m. In order to support the main cave excavation and support, surrounding rock grouting and other activities, a slant shaft construction material hoisting system is installed in the branch cave, the following are the hoisting system parameters calibration and system design process, respectively.

4.2. Lifting System Parameter Calibration

4.2.1. Wire Rope Parameters Calibration

Hoisting system wire rope calculation parameters are shown in

Table 2. Calculated parameters of steel wire rope.

Calculation Parameters	Takes Values
Wire rope breaking tension $Q_q$ (KN)	490.29
Quality of wire rope per meter $q$ (kg)	2.75
Lift tilt angle $\theta$ (°)	22
Transporters enhance cargo quality $G$ (t)	9.1
Transporter quality $G_0$ (t)	6.5
Skip operation resistance coefficient $\omega$	0.015
Coefficient of resistance of steel wire rope operation ${\omega }^{\text{'}}$	0.2
Wire rope length $L_c$ (m)	330
Safety factor $m$	7.0
Does it meet the requirements	$m$ > 6.5, Meet the requirements

.

The calculated parameters into Formula (1): safety factor $m$ = 7.0 > 6.5 wire rope maximum static tension $F_j$ = 6652.8 N, by the above calculation, wire rope safety factor to meet the specification requirements. Therefore, according to the wire rope maximum breaking tension value $Q_q$ = 490.29 KN, the choice of natural fiber core wire rope 6 × 7 + NF wire rope, its design parameters for the diameter $d$ = 28 mm, wire rope per meter quality $q$ = 2.75 kg/m.

4.2.2. Roller Parameter Calibration

The calculated parameters of the hoisting system drum are shown in

Table 3. Calculated parameters of rollers.

Calculation Parameters	Takes Values
Wire rope diameter $d$ (mm)	28
Number of winding layers $k$	3
Lift height $H$ (m)	620
Wrong number of rope loops $n^{\text{'}}$	4
Wire Rope Loop Clearance $\epsilon$ (mm)	2

.

Substitute the calculated parameters into Equations (2)–(4) to get the drum diameter $D$ ≥ 1680 mm, average winding radius $D_p$ = 20,487.3 mm, drum width $B$ = 628 mm. According to the calculation result, choose the drum with diameter $D$ = 2000 mm, width $B$ = 1500 m. After the selection, the inclined shaft hoisting system selects single drum hoist JK-2 × 1.5 P type hoist, whose maximum static tension is 60 kN and rope capacity is 964 m.

4.2.3. Calibration of Motor and Skywheel Parameters

The calculated parameters of the hoisting system motor and the skywheel are shown in

Table 4. Calculated parameters of motor and skywheel.

Calculation Parameters	Takes Values
Reduction ratio of speed reducer $i$	31.5
Motor speed $r$ (r/min)	740
Motor power reserve factor $K$	1.2
Reducer transmission efficiency $\eta$	0.85
Work condition factor $R$	1.5
Safety factor $S$	1.5

.

Substitute the calculated parameters into the Formulas (4)–(7) to get the motor lifting speed $V_m$ = 2.45 m/s < 5 m/s, to meet the specification requirements. Motor lifting power $N$ = 213.7 KW, reducer permissible input power $PC$ = 562.5 KW. According to the calculation results, YTS355L2-8 motor with power $P$ = 250 KW, voltage 380 V, speed $n$ = 740 r/min is selected.

The calculated parameters are substituted into the Formulas (8) and (9) to obtain the diameter of the wheel of $D_t$ $\ge$ 1200 mm and the depth of the wheel groove of $h$ = 50 mm, so the wheel of diameter $D_t$ = 1.2 m and the depth of the wheel groove $h$ = 50 mm is chosen.

In summary, the lifting system parameters calibration scheme is shown in

Table 5. Calibration scheme for lifting system parameters.

Parts	Selection
Wire Rope	6 × 7 + NF Type
Rollers	Diameter 2000 mm, width 1500 mm
Hoist	Single cylinder JK-2 × 1.5 P type
Motor	YTS355L2-8 type
Overhead Wheel	Diameter 1.2 m, Wheel groove depth 50 mm

.

4.3. System Design

4.3.1. Control System Design

In terms of the control system design, the conventional electronic control system is not selected because of high energy consumption and poor speed regulation. Although the PCL electronic control system is small and versatile, it is costly, technically complex and requires professional training; thus, it is also not considered. Therefore, due to the comprehensive cost, equipment energy consumption, speed control performance and other factors, the choice is the frequency conversion electronic control method as the control system design.

The selected inverter electric control system mainly includes two major parts: PCL cabinet and integrated operation desk. The main equipment includes an EMC filter reactor, main contactor, dual Siemens PLC, main command controller, isolation control transformer 380 V/220 V, etc. The control system adopts vector the control mode and the input power supply voltage is 15 KV, which can guarantee 220% output torque when low frequency operation is used, and has advantages in energy saving and stable motor performance.

The monitoring system is designed to be divided into two parts according to the construction needs of the inclined shaft, which are the data center and the terminal monitoring equipment. In summary, the main equipment selected for the main control and monitoring system is shown in

Table 6. Main control system main equipment.

Serial Number	Name Model	Main Device Composition
Master Control System	PCL cabinet	EMC filter reactor
		Dual power supply molded case circuit breaker
		Main contactor
		Motor protection quick fuse
		Isolation control transformer 380 V/220 V
	All-in-one operation desk	Control contactors
		Dual Siemens PLC
		Proportional amplifier
		Switching power supply
		Relays
		Master command controller
Monitoring System	Data Center	Optical Terminals
		Cloud Station
		Cloud Station Decoder
	Monitoring equipment	Current monitor
		Mine car speed monitor
		Mine car travel distance monitor

.

4.3.2. Safety Protection Device Design

For the project after research, the current domestic production of sports car protection device, the maximum rated impact resistance energy of 2.5 × 106 J. After comparative analysis, the ZDC30-2.5 anti-cars device is chosen; its main parameters are shown in

Table 7. Parameters of running car guards.

Calculation Parameters	Takes Values
Rated voltage $U$ (W)	380
Motor power $P$ (KW)	1.5
Blocking bar impact energy resistance $E$ (KJ)	2.5 × 106
Transport material full load $\mathrm{m}$/t	15.6
Winch initial speed $v_0$ ($\mathrm{m}\cdot {\mathrm{s}}^{-1}$)	0
Operating resistance coefficient $\mu$	0.015
Inclined shaft inclination $\alpha$/(°)	22
Max. operating speed of winch $v$ ($\mathrm{m}\cdot {\mathrm{s}}^{-1}$)	4.6
Running height $H^{\text{'}}$ (m)	1.5
Barrier operation speed $v^{\text{'}}$ ($\mathrm{m}\cdot {\mathrm{s}}^{-1}$)	0.42

.

Substitute the above parameters into Formulas (12) and (13) to calculate: the maximum distance to install the anti-cars device $L_{\max }$ = 39.9 m, open the minimum distance in advance of the barrier = 16.5 m. According to the above calculation results, the inclined shaft needs to lay out an anti-cars device every 39.9 m and set the barrier at $L_{\min }$ = 16.5 m from the sports car slide, see Figure 8 for the specific schematic diagram.

When the phenomenon of running car and slipping car occurs, the anti-cars device first starts to work, holds the track below under the drive of the guide bar and completes holding the track to make the mine car stop running. If the mine car continues to run on the track, the stopper starts to work to stop the mine car reliably, so as to effectively avoid the occurrence of accidents.

5. Conclusions

(1) To address the problem of material transportation in slant shaft construction, a parameterized calibration scheme for a slant shaft hoisting system is proposed to determine the structural parameters of each component, and the parameterized calibration scheme is introduced into the Dianzhong water diversion project to verify the results, which can provide a quantitative basis for the parameterized design of hoisting system in related projects.

(2) Through the design of the hoisting system structure and functional analysis, the design of a reasonable slope hoisting control system, monitoring system and safety protection device, the results show that the inverter electronic control system has advantages in energy saving and motor performance stability, and the safety protection device can effectively prevent the occurrence of vehicle slip and mine car overturning accidents to ensure the safety of slope hoisting system operation.