# Research on Dynamic Characteristics and Compensation of Wire Rope Tension and Load Measurement Based on Hydraulic Connection Device

Authors: Di Song; Gui-Yun Xu; Gao-Yang Lei; Xiao-Guang Zhang; Bao-Lai Tian
Journal: Shock and Vibration
 (2019)

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## Abstract

During the operation of hoist, the speed and acceleration of each wire rope are inconsistent and the inertia force is changed due to the wear of the friction pad on the drum, which makes an impact on the cylinder of the tension balance hydraulic connection device and aggravates the flow pressure loss. It results in the nonlinear friction force between the piston and cylinder and affects the accuracy of wire rope tension and load measured by an oil pressure sensor which is installed on the tension balance hydraulic connecting device. In this paper, the simulation model of the tension balanced hydraulic connecting device is established by AMESim software, and the hydraulic dynamic response under different pressures, flow rates, and speed of a single hydraulic cylinder and tension balanced hydraulic connecting device is analyzed. The Leuven friction model is used to compensate the pressure loss along the course and local pressure loss and calculate the friction force, where specific parameters are determined by experiments. The real-time compensation experiment of the tension balance hydraulic connecting device proves that the device effectively improves the accuracy of wire rope tension and load monitoring.


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## Body

## 1. Introduction

The hoist is an important part of the mine hoisting system which can be divided into single winding type and multirope friction type, and multirope friction hoist is most widely used in coal mines at present [1, 2]. To maintain the safe operation of the hoist, it is necessary to measure the wire rope tension and load.In the paper, the wire rope tension and load can be measured by the oil pressure sensor installed on the tension balance hydraulic connection device, which is connected with the hoisting container and the wire ropes of multirope friction hoist [3]. The structure of tension balance hydraulic connection device is shown in Figure 1(a). The device is composed of four separate tension measuring devices, which are connected together by connecting device composed of tubing and valves [4]. Oil pressure sensors are installed on each cylinder of tension measuring devices by external hydraulic pipelines to monitor oil pressure. The oil pressure of each cylinder multiplied by the working area of the piston can be conversed to the tension of each wire rope [5, 6]. Initially, the pressure of each cylinder keeps equal. When the tension of each wire rope is inconsistent due to the different elongation of each rope, the pressure balance of each cylinder is broken. The wire rope with the maximum tension is greater than the initial pressure, and this wire rope will first pull the piston rod to increase the wire rope length and then reduce the tension. Then, the oil in the maximum pressure cylinder passes through connecting device to the minimum pressure cylinder, which pushes the piston rod, reduces the length of the wire rope, and increases the tension. Finally, the tension of each wire rope and the pressure of each cylinder are equal. Therefore, the device can balance the tension of each wire rope and buffer the vibration and impact of the wire rope [7].Figure 1
Structure of wire rope tension balance hydraulic connection device. 1, wedge-shaped rope ring; 2, medium plate; 3, top connecting pin; 4, baffle; 5, pressure plate; 6, side plate; 7, connecting cylinder; 8, connecting device; 9, pressure block; l0, middle connecting pin; 11, reversing fork; 12, connecting pin.
(a)
(b)Domestic and foreign scholars have done a lot of work on monitoring the wire rope tension and load. In foreign countries, the wire rope tension and load measurement method measured by the sensor or other instruments have been developed in many countries [8–10]. O’Dogherty [11] designed an octagonal ring dynamometer to measure two orthogonal forces and a moment applied in the plane of the ring through appropriately mounted strain gauge bridges and presented a fundamental formulate for the moment and strain distributions in circular, octagonal, and extended octagonal rings. In 2012, Jin and Zhang [12] designed a tension sensor for the hoist wire rope using the strain gauge as the measurement principle and the spoke as the flexible structure and adopted configuration software as detection system software to realize online monitoring of the tension. Daifuku et al. [6] developed a tension meter for wire rope and lashing belt of a postmountable type by which the magnitude of their tension in use can be evaluated. Zhang and Sun [13] used the method of variables separation and generalized coordinates method to analyze the characteristics of the mine hoist wire rope tension and designed a steel rope tension online monitoring system. Fan and Yang [14] derived the calculation formula of wire-rope tension based on inhomogeneous chord vibration and developed the test method of hoist wire-rope tension by using the basic principles of the wire-rope tension measurement with method of vibration.For measuring the wire rope tension and load by installing oil sensors on a hydraulic balancing device, there are usually two methods: conversing tension to pressure and measuring oil pressure directly [15, 16]. The former method measures the pressure between the piston rod and the pressure block and converts the tension of the wire rope into pressure, which is shown in Figure 1(b). However, the results measured by this method have severe fluctuation and noise, which cannot effectively reflect the tension and load. In this paper, oil pressure sensor installed in tension balance hydraulic connection device is used to measure the wire rope tension and load, which can effectively reduce fluctuation of wire rope. The wire rope tension and load can be measured accurately by the effective compensation of the oil pressure and friction force through the Leuven friction model [17].


## 2. Mathematical Model and Dynamic Response of the Connection Device

### 2.1. Mathematical Model of the Hydraulic Connection

When the influence of wire rope mass on tension is neglected, the wire rope and the hydraulic connecting device can be regarded as a spring-damper system without mass, in which the wire rope is regarded as a spring system and the hydraulic cylinder of the hydraulic connecting device is regarded as a damper system. The system is shown in Figure2.Figure 2
Mathematical model of the hydraulic connection.c
′ represents the damping coefficient of liquid flow in the pipeline, a denotes the acceleration, c represents the damping coefficient of piston movement, xi denotes the displacement of piston in the i hydraulic cylinder relative to the initial position of piston, Fi denotes the force of the piston rod of the hydraulic cylinder, m represents the mass of the piston, m2 represents the mass of hydraulic cylinder body, pi is the pressure of the rod free cavity, and Pi is the force of hydraulic cylinder body caused by lifting load. Take one of the hydraulic cylinders as an example:The dynamic equation of piston force can be described as follows:(1)ma=Fi−piA−cx˙i.When the hydraulic cylinder piston massm is ignored, equation (1) can be described as follows:(2)Fi=piA+cx˙i.The dynamic equation of hydraulic cylinder body force can be described as follows:(3)m2x¨′=piA−Pi+cx˙i.When the hydraulic cylinder body massm2 is ignored, equation (3) can be described as follows:(4)Pi=piA+cx˙i.Through equation (2) and equation (4), there is an approximate equality between the tension of the wire rope and the lifting load during the operation of the hoisting system.


### 2.2. Hydraulic Dynamic Response of the Hydraulic Connection Device

When the tension of each wire rope is not equal, the displacement of the corresponding cylinder piston and the pressure of the working chamber are changed. When the tension is adjusted by the hydraulic connecting device, the oil in the cylinder will flow from the high-pressure cylinder to the low-pressure one, which causes pressure impact during the flow passing through the pipeline and valve. Taking the parallel connection of two cylinders as an example, the pressure of two cylinders isp1, p2 and the volume is V1, V2. The continuity equation of flowing oil is expressed as follows:(5)dV2dt=V2βdp2dt,dV2dt=au¯,where a means the average cross-sectional area of pipes and F=σ0z+σ1dz/dt+σ2v denotes the velocity of flowing oil in pipeline. According to Poiseuille formula, the friction resistance of pipeline in laminar flow state is as follows:(6)f=128μlπd4a2u,where μ represents fluid viscosity, d means average pipe diameter, and l denotes the pipe length. The equation of liquid force in parallel pipes is as follows:(7)ρaldu¯dt=p1a−p2a−f.Combining equations (5)–(7), the following equation can be obtained:(8)4ρlV2πβd2d2p2dt2+128μlV2πβd4dp2dt+p2=p1,where ρ represents oil density in the cylinder and β means liquid bulk modulus. This is a typical two-order vibration. The natural frequency of the system is as follows:(9)wn=d2πβρlV2.The damping ratio of the system is(10)ξ=32ud3V2lπdβ.The typical transfer function of the two order system is(11)Gs=P2sP1s=11/wns2+2ξ/wns+1.In the simulation, the density, kinematic viscosity, piston diameter, cylinder length, spool diameter, pipeline length, and dynamic viscosity are 900 kg/m3, 46 mm2/s, 80 mm, 800 mm, 6 mm, 1000 mm, and 0.0414 kg/ms, respectively. The Bode diagram is shown in Figure 3.Figure 3
Bode diagram.According to the above equations and Figure3, wn increases with the decrease of the length (l) of the pipeline and the volume (V2) and the increase of the diameter (d) of the pipeline. Adjusting these three parameters can promote the natural frequency and the damping ratio of the system. In order to improve the stability of hydraulic connecting device in the damped second-order oscillation system, the resonance frequency should be avoided as far as possible.


## 2.1. Mathematical Model of the Hydraulic Connection

When the influence of wire rope mass on tension is neglected, the wire rope and the hydraulic connecting device can be regarded as a spring-damper system without mass, in which the wire rope is regarded as a spring system and the hydraulic cylinder of the hydraulic connecting device is regarded as a damper system. The system is shown in Figure2.Figure 2
Mathematical model of the hydraulic connection.c
′ represents the damping coefficient of liquid flow in the pipeline, a denotes the acceleration, c represents the damping coefficient of piston movement, xi denotes the displacement of piston in the i hydraulic cylinder relative to the initial position of piston, Fi denotes the force of the piston rod of the hydraulic cylinder, m represents the mass of the piston, m2 represents the mass of hydraulic cylinder body, pi is the pressure of the rod free cavity, and Pi is the force of hydraulic cylinder body caused by lifting load. Take one of the hydraulic cylinders as an example:The dynamic equation of piston force can be described as follows:(1)ma=Fi−piA−cx˙i.When the hydraulic cylinder piston massm is ignored, equation (1) can be described as follows:(2)Fi=piA+cx˙i.The dynamic equation of hydraulic cylinder body force can be described as follows:(3)m2x¨′=piA−Pi+cx˙i.When the hydraulic cylinder body massm2 is ignored, equation (3) can be described as follows:(4)Pi=piA+cx˙i.Through equation (2) and equation (4), there is an approximate equality between the tension of the wire rope and the lifting load during the operation of the hoisting system.


## 2.2. Hydraulic Dynamic Response of the Hydraulic Connection Device

When the tension of each wire rope is not equal, the displacement of the corresponding cylinder piston and the pressure of the working chamber are changed. When the tension is adjusted by the hydraulic connecting device, the oil in the cylinder will flow from the high-pressure cylinder to the low-pressure one, which causes pressure impact during the flow passing through the pipeline and valve. Taking the parallel connection of two cylinders as an example, the pressure of two cylinders isp1, p2 and the volume is V1, V2. The continuity equation of flowing oil is expressed as follows:(5)dV2dt=V2βdp2dt,dV2dt=au¯,where a means the average cross-sectional area of pipes and F=σ0z+σ1dz/dt+σ2v denotes the velocity of flowing oil in pipeline. According to Poiseuille formula, the friction resistance of pipeline in laminar flow state is as follows:(6)f=128μlπd4a2u,where μ represents fluid viscosity, d means average pipe diameter, and l denotes the pipe length. The equation of liquid force in parallel pipes is as follows:(7)ρaldu¯dt=p1a−p2a−f.Combining equations (5)–(7), the following equation can be obtained:(8)4ρlV2πβd2d2p2dt2+128μlV2πβd4dp2dt+p2=p1,where ρ represents oil density in the cylinder and β means liquid bulk modulus. This is a typical two-order vibration. The natural frequency of the system is as follows:(9)wn=d2πβρlV2.The damping ratio of the system is(10)ξ=32ud3V2lπdβ.The typical transfer function of the two order system is(11)Gs=P2sP1s=11/wns2+2ξ/wns+1.In the simulation, the density, kinematic viscosity, piston diameter, cylinder length, spool diameter, pipeline length, and dynamic viscosity are 900 kg/m3, 46 mm2/s, 80 mm, 800 mm, 6 mm, 1000 mm, and 0.0414 kg/ms, respectively. The Bode diagram is shown in Figure 3.Figure 3
Bode diagram.According to the above equations and Figure3, wn increases with the decrease of the length (l) of the pipeline and the volume (V2) and the increase of the diameter (d) of the pipeline. Adjusting these three parameters can promote the natural frequency and the damping ratio of the system. In order to improve the stability of hydraulic connecting device in the damped second-order oscillation system, the resonance frequency should be avoided as far as possible.


## 3. Simulation of Hydraulic Connection Device

The hydraulic model of single hydraulic system and hydraulic connecting device are established and simulated by using AMESim under the influence of drum and tail rope. The dynamic characteristics of hydraulic connecting device are analyzed under different pressure and flow rate, and the effects of load change on the pressure, flow, and flow rate of connecting device are studied [18]. It can reflect the influence of wire rope vibration on the measurement of tension and load and pave the way for the selection of compensation model for compensating the loss of pressure and flow [19].


### 3.1. Modeling and Simulation Results of Single Hydraulic System

#### 3.1.1. AMESim Modeling of Single Hydraulic System

In Figure4, it can be seen that the hydraulic simulation system consists of electromagnetic directional valve, hydraulic cylinder, and overflow valves in the return circuit of the oil. The load can be simulated by adjusting the pressure of the overflow valves.Figure 4
AMESim modeling of the single hydraulic system. 1, oil tank; 2, oil filter; 3, motor; 4, hydraulic pump; 5, signal source 1; 6, signal source 2; 7, balance cylinder; 8, loading cylinder; 9, electromagnetic directional valve; 10, overflow valve 1; 11, overflow valve 2.In the simulation, the rated pressure of the pump is 12 MPa and the rated flow rate is 20 L/min, and the actual flow rate is adjusted as required. The hydraulic cylinder isϕ100mm×ϕ60mm×1000mm.


#### 3.1.2. Simulation of Shuttling of Single Hydraulic Cylinder

(1)
The pressure characteristics of hydraulic cylinders under different load pressures.
The load pressure is set to 11 MPa, 9 MPa, 7 MPa, 5 MPa, 3 MPa, and 1 MPa, respectively, through the different backpressure of overflow valves in the return circuit of the oil. According to Figure5, the pressure loss under different backpressure conditions is 0.36 Mpa, which is independent of working pressure. Taking the backpressure curve of 11 MPa as an example, the maximum fluctuation pressure is 11.86 MPa during 0.2 s and the pressure is stable at 11.36 MPa after 0.3 s. The stable pressure is larger by 0.36 MPa than the backpressure load pressure, which is the pressure loss.
There is friction resistance in the piston of the balancing cylinder, which influents the pressure. In Figure6, it is shown that when the friction becomes smaller, the pressure fluctuation and the fluctuation time become greater and longer.
(2)
The pressure characteristics of hydraulic cylinder under different flow rate.
The flow rate of the hydraulic pump is set to 20 L/min, 15 L/min, 10 L/min, and 5 L/min, respectively, with the 10 MPa load pressure.
Figure7 shows that the pressure loss varies with flow rate. The pressure fluctuation amplitude of cylinder is proportional to the flow rate of the hydraulic pump, and the time required to balance the pressure in the cylinder to reach the load pressure is inversely proportional to it.
(3)
The pressure characteristics of the hydraulic cylinder under reciprocating motion.
The motion direction of the piston of the cylinder changes irregularly under actual working conditions. The pressure of cylinder is affected by the change of piston direction with the frictional resistance of the cylinder.
According to Figure8, the two curves in the diagram are the simulation of two cases: frictional resistance exists or not. The pressure of cylinder cavity fluctuates when the cylinder reverses at 1 s and 2 s.Figure 5
Pressure changes of the cylinder without rod chamber.Figure 6
Effect of frictional resistance on the pressure of the rodless cavity.
(a)
(b)Figure 7
Pressure curves of rodless cavity under different flow rates.Figure 8
Pressure changes under frictional resistance.


### 3.2. Modeling and Simulation Results of Hydraulic Connection Device

#### 3.2.1. Modeling of Hydraulic Connection Device

In Figure9, the hydraulic connection device is established by using AMESim, where the friction wheel is a standard circle. In order to simulate the excitation of different wear of four rope grooves of driving drum on hoist wire rope, the excitation change caused by the wear of the liner is transformed into the force excitation in the vertical direction of the connecting device.Figure 9
Simulation of the hydraulic connection device. 1, roller; 2, load signal source; 3, balancing cylinder; 4, friction mass block; 5, stop valve; 6, spring damping; 7, tail rope.


#### 3.2.2. Simulation Analysis of Hydraulic Connection Device

When the hydraulic connecting device works, the oil pressure and flow impact occur in the pipeline inevitably. It brings a great impact on the stability of the hydraulic system and the accuracy of wire rope load detection.(1)
Figure10 shows the input curve of four balancing cylinder signal load sources. The four load signals of 0∼3 s increase from around 2000 N to about 5000 N in different slopes. The load changes suddenly to more than 6000 N at 3 s and remains unchanged later.(2)
The characteristic of oil tube is not considered. After removing all the stop valves 5 in the simulation model of Figure9, the simulation curve of the four cylinders without rod chamber is shown in Figure 11. It shows that no matter how load changes, the pressure in the four balanced cylinders keeps the same.(3)
The characteristic of oil tube is considered. There is a stop valve on each bypass oil tube of the connecting device in Figure9. The pressure changing curve of hydraulic cylinder without rod chamber in connection device is shown in Figure 12. Comparing with the load signal of Figure 10, the hydraulic oil pressures in the four cylinders without rod chamber in Figure 12(a) are adjusted by the connecting device and maintained the same.However, it can be seen from the Figure12(b) that when the load changes suddenly, it will impact the balance cylinder and cause the difference pressure in the cylinder instantly. It can be regarded as a difference between the loads of the four wire ropes. According to the Figure 12(b), the fluctuation is the largest at 3.1 s time, and then the cylinder pressure remains stable. The pressure impact of hydraulic cylinder cannot be ignored, which affects the dynamic performance of cylinder and the accuracy of load detection.(4)
Figure13 shows the flow rate curve of hydraulic cylinder without rod chamber in the connection device. The flow of the first and the third cylinders vary during 2.88 s to 3.01 s. The flow of the first and the third cylinder decreases first and then increases. The flow of the second cylinder and the fourth cylinder varies greatly and becomes unstable during 2.88 s to 3.01 s. It is explained that pressure shock is the main cause of the flow change in the rodless chamber.(5)
Figure14 shows the changing displacement curve of four balancing cylinders in the hydraulic connecting device. Because the load of the first cylinder and the fourth cylinder is larger during 0 s to 3 s, the cylinder produces positive movement and the hydraulic oil discharges. The piston displacements of the four cylinders are 10 mm, −10 mm, −18 mm, and 20 mm, respectively. When the load is changed suddenly during 3 s to 6 s, the load of the second cylinder is the largest and the load of the first cylinder is the smallest. Therefore, the piston of the fourth cylinder produces the maximum displacement of 26 mm. The displacement of the third and fourth cylinders is 10 mm and −10 mm, and the displacement of the first cylinder is −26 mm.Figure 10
Input curve of signal source load.Figure 11
Pressure of four cylinders without rod chamber.Figure 12
Pressure variation curves of each hydraulic cylinder without rod chamber in the connection device.
(a)
(b)Figure 13
Flow rate curve of the hydraulic cylinder without rod chamber in the connection device.
(a)
(b)Figure 14
Displacement curve of the cylinder piston.Comparing with the curve of signal source load in Figure10, when the load changes drastically during 0–0.2 s and 2.8–3.4 s, it will cause a greater pressure impact to the hydraulic connecting device. If the loads of the four cylinders are obviously different, the pressure of the four cylinders are adjusted by connecting pipelines to ensure the same internal pressure of the rodless chamber, which is shown in Figure 12.The dynamic characteristics of the hydraulic balancing device show that it plays an important role of balancing oil pressure, wire tension, and load to a certain extent. It seriously affects the accurate monitoring of wire rope load which is affected by the load changing, the friction between piston and hydraulic, and the pressure loss caused by hydraulic flow.


## 3.1. Modeling and Simulation Results of Single Hydraulic System

### 3.1.1. AMESim Modeling of Single Hydraulic System

In Figure4, it can be seen that the hydraulic simulation system consists of electromagnetic directional valve, hydraulic cylinder, and overflow valves in the return circuit of the oil. The load can be simulated by adjusting the pressure of the overflow valves.Figure 4
AMESim modeling of the single hydraulic system. 1, oil tank; 2, oil filter; 3, motor; 4, hydraulic pump; 5, signal source 1; 6, signal source 2; 7, balance cylinder; 8, loading cylinder; 9, electromagnetic directional valve; 10, overflow valve 1; 11, overflow valve 2.In the simulation, the rated pressure of the pump is 12 MPa and the rated flow rate is 20 L/min, and the actual flow rate is adjusted as required. The hydraulic cylinder isϕ100mm×ϕ60mm×1000mm.


### 3.1.2. Simulation of Shuttling of Single Hydraulic Cylinder

(1)
The pressure characteristics of hydraulic cylinders under different load pressures.
The load pressure is set to 11 MPa, 9 MPa, 7 MPa, 5 MPa, 3 MPa, and 1 MPa, respectively, through the different backpressure of overflow valves in the return circuit of the oil. According to Figure5, the pressure loss under different backpressure conditions is 0.36 Mpa, which is independent of working pressure. Taking the backpressure curve of 11 MPa as an example, the maximum fluctuation pressure is 11.86 MPa during 0.2 s and the pressure is stable at 11.36 MPa after 0.3 s. The stable pressure is larger by 0.36 MPa than the backpressure load pressure, which is the pressure loss.
There is friction resistance in the piston of the balancing cylinder, which influents the pressure. In Figure6, it is shown that when the friction becomes smaller, the pressure fluctuation and the fluctuation time become greater and longer.
(2)
The pressure characteristics of hydraulic cylinder under different flow rate.
The flow rate of the hydraulic pump is set to 20 L/min, 15 L/min, 10 L/min, and 5 L/min, respectively, with the 10 MPa load pressure.
Figure7 shows that the pressure loss varies with flow rate. The pressure fluctuation amplitude of cylinder is proportional to the flow rate of the hydraulic pump, and the time required to balance the pressure in the cylinder to reach the load pressure is inversely proportional to it.
(3)
The pressure characteristics of the hydraulic cylinder under reciprocating motion.
The motion direction of the piston of the cylinder changes irregularly under actual working conditions. The pressure of cylinder is affected by the change of piston direction with the frictional resistance of the cylinder.
According to Figure8, the two curves in the diagram are the simulation of two cases: frictional resistance exists or not. The pressure of cylinder cavity fluctuates when the cylinder reverses at 1 s and 2 s.Figure 5
Pressure changes of the cylinder without rod chamber.Figure 6
Effect of frictional resistance on the pressure of the rodless cavity.
(a)
(b)Figure 7
Pressure curves of rodless cavity under different flow rates.Figure 8
Pressure changes under frictional resistance.


## 3.1.1. AMESim Modeling of Single Hydraulic System

In Figure4, it can be seen that the hydraulic simulation system consists of electromagnetic directional valve, hydraulic cylinder, and overflow valves in the return circuit of the oil. The load can be simulated by adjusting the pressure of the overflow valves.Figure 4
AMESim modeling of the single hydraulic system. 1, oil tank; 2, oil filter; 3, motor; 4, hydraulic pump; 5, signal source 1; 6, signal source 2; 7, balance cylinder; 8, loading cylinder; 9, electromagnetic directional valve; 10, overflow valve 1; 11, overflow valve 2.In the simulation, the rated pressure of the pump is 12 MPa and the rated flow rate is 20 L/min, and the actual flow rate is adjusted as required. The hydraulic cylinder isϕ100mm×ϕ60mm×1000mm.


## 3.1.2. Simulation of Shuttling of Single Hydraulic Cylinder

(1)
The pressure characteristics of hydraulic cylinders under different load pressures.
The load pressure is set to 11 MPa, 9 MPa, 7 MPa, 5 MPa, 3 MPa, and 1 MPa, respectively, through the different backpressure of overflow valves in the return circuit of the oil. According to Figure5, the pressure loss under different backpressure conditions is 0.36 Mpa, which is independent of working pressure. Taking the backpressure curve of 11 MPa as an example, the maximum fluctuation pressure is 11.86 MPa during 0.2 s and the pressure is stable at 11.36 MPa after 0.3 s. The stable pressure is larger by 0.36 MPa than the backpressure load pressure, which is the pressure loss.
There is friction resistance in the piston of the balancing cylinder, which influents the pressure. In Figure6, it is shown that when the friction becomes smaller, the pressure fluctuation and the fluctuation time become greater and longer.
(2)
The pressure characteristics of hydraulic cylinder under different flow rate.
The flow rate of the hydraulic pump is set to 20 L/min, 15 L/min, 10 L/min, and 5 L/min, respectively, with the 10 MPa load pressure.
Figure7 shows that the pressure loss varies with flow rate. The pressure fluctuation amplitude of cylinder is proportional to the flow rate of the hydraulic pump, and the time required to balance the pressure in the cylinder to reach the load pressure is inversely proportional to it.
(3)
The pressure characteristics of the hydraulic cylinder under reciprocating motion.
The motion direction of the piston of the cylinder changes irregularly under actual working conditions. The pressure of cylinder is affected by the change of piston direction with the frictional resistance of the cylinder.
According to Figure8, the two curves in the diagram are the simulation of two cases: frictional resistance exists or not. The pressure of cylinder cavity fluctuates when the cylinder reverses at 1 s and 2 s.Figure 5
Pressure changes of the cylinder without rod chamber.Figure 6
Effect of frictional resistance on the pressure of the rodless cavity.
(a)
(b)Figure 7
Pressure curves of rodless cavity under different flow rates.Figure 8
Pressure changes under frictional resistance.


## 3.2. Modeling and Simulation Results of Hydraulic Connection Device

### 3.2.1. Modeling of Hydraulic Connection Device

In Figure9, the hydraulic connection device is established by using AMESim, where the friction wheel is a standard circle. In order to simulate the excitation of different wear of four rope grooves of driving drum on hoist wire rope, the excitation change caused by the wear of the liner is transformed into the force excitation in the vertical direction of the connecting device.Figure 9
Simulation of the hydraulic connection device. 1, roller; 2, load signal source; 3, balancing cylinder; 4, friction mass block; 5, stop valve; 6, spring damping; 7, tail rope.


### 3.2.2. Simulation Analysis of Hydraulic Connection Device

When the hydraulic connecting device works, the oil pressure and flow impact occur in the pipeline inevitably. It brings a great impact on the stability of the hydraulic system and the accuracy of wire rope load detection.(1)
Figure10 shows the input curve of four balancing cylinder signal load sources. The four load signals of 0∼3 s increase from around 2000 N to about 5000 N in different slopes. The load changes suddenly to more than 6000 N at 3 s and remains unchanged later.(2)
The characteristic of oil tube is not considered. After removing all the stop valves 5 in the simulation model of Figure9, the simulation curve of the four cylinders without rod chamber is shown in Figure 11. It shows that no matter how load changes, the pressure in the four balanced cylinders keeps the same.(3)
The characteristic of oil tube is considered. There is a stop valve on each bypass oil tube of the connecting device in Figure9. The pressure changing curve of hydraulic cylinder without rod chamber in connection device is shown in Figure 12. Comparing with the load signal of Figure 10, the hydraulic oil pressures in the four cylinders without rod chamber in Figure 12(a) are adjusted by the connecting device and maintained the same.However, it can be seen from the Figure12(b) that when the load changes suddenly, it will impact the balance cylinder and cause the difference pressure in the cylinder instantly. It can be regarded as a difference between the loads of the four wire ropes. According to the Figure 12(b), the fluctuation is the largest at 3.1 s time, and then the cylinder pressure remains stable. The pressure impact of hydraulic cylinder cannot be ignored, which affects the dynamic performance of cylinder and the accuracy of load detection.(4)
Figure13 shows the flow rate curve of hydraulic cylinder without rod chamber in the connection device. The flow of the first and the third cylinders vary during 2.88 s to 3.01 s. The flow of the first and the third cylinder decreases first and then increases. The flow of the second cylinder and the fourth cylinder varies greatly and becomes unstable during 2.88 s to 3.01 s. It is explained that pressure shock is the main cause of the flow change in the rodless chamber.(5)
Figure14 shows the changing displacement curve of four balancing cylinders in the hydraulic connecting device. Because the load of the first cylinder and the fourth cylinder is larger during 0 s to 3 s, the cylinder produces positive movement and the hydraulic oil discharges. The piston displacements of the four cylinders are 10 mm, −10 mm, −18 mm, and 20 mm, respectively. When the load is changed suddenly during 3 s to 6 s, the load of the second cylinder is the largest and the load of the first cylinder is the smallest. Therefore, the piston of the fourth cylinder produces the maximum displacement of 26 mm. The displacement of the third and fourth cylinders is 10 mm and −10 mm, and the displacement of the first cylinder is −26 mm.Figure 10
Input curve of signal source load.Figure 11
Pressure of four cylinders without rod chamber.Figure 12
Pressure variation curves of each hydraulic cylinder without rod chamber in the connection device.
(a)
(b)Figure 13
Flow rate curve of the hydraulic cylinder without rod chamber in the connection device.
(a)
(b)Figure 14
Displacement curve of the cylinder piston.Comparing with the curve of signal source load in Figure10, when the load changes drastically during 0–0.2 s and 2.8–3.4 s, it will cause a greater pressure impact to the hydraulic connecting device. If the loads of the four cylinders are obviously different, the pressure of the four cylinders are adjusted by connecting pipelines to ensure the same internal pressure of the rodless chamber, which is shown in Figure 12.The dynamic characteristics of the hydraulic balancing device show that it plays an important role of balancing oil pressure, wire tension, and load to a certain extent. It seriously affects the accurate monitoring of wire rope load which is affected by the load changing, the friction between piston and hydraulic, and the pressure loss caused by hydraulic flow.


## 3.2.1. Modeling of Hydraulic Connection Device

In Figure9, the hydraulic connection device is established by using AMESim, where the friction wheel is a standard circle. In order to simulate the excitation of different wear of four rope grooves of driving drum on hoist wire rope, the excitation change caused by the wear of the liner is transformed into the force excitation in the vertical direction of the connecting device.Figure 9
Simulation of the hydraulic connection device. 1, roller; 2, load signal source; 3, balancing cylinder; 4, friction mass block; 5, stop valve; 6, spring damping; 7, tail rope.


## 3.2.2. Simulation Analysis of Hydraulic Connection Device

When the hydraulic connecting device works, the oil pressure and flow impact occur in the pipeline inevitably. It brings a great impact on the stability of the hydraulic system and the accuracy of wire rope load detection.(1)
Figure10 shows the input curve of four balancing cylinder signal load sources. The four load signals of 0∼3 s increase from around 2000 N to about 5000 N in different slopes. The load changes suddenly to more than 6000 N at 3 s and remains unchanged later.(2)
The characteristic of oil tube is not considered. After removing all the stop valves 5 in the simulation model of Figure9, the simulation curve of the four cylinders without rod chamber is shown in Figure 11. It shows that no matter how load changes, the pressure in the four balanced cylinders keeps the same.(3)
The characteristic of oil tube is considered. There is a stop valve on each bypass oil tube of the connecting device in Figure9. The pressure changing curve of hydraulic cylinder without rod chamber in connection device is shown in Figure 12. Comparing with the load signal of Figure 10, the hydraulic oil pressures in the four cylinders without rod chamber in Figure 12(a) are adjusted by the connecting device and maintained the same.However, it can be seen from the Figure12(b) that when the load changes suddenly, it will impact the balance cylinder and cause the difference pressure in the cylinder instantly. It can be regarded as a difference between the loads of the four wire ropes. According to the Figure 12(b), the fluctuation is the largest at 3.1 s time, and then the cylinder pressure remains stable. The pressure impact of hydraulic cylinder cannot be ignored, which affects the dynamic performance of cylinder and the accuracy of load detection.(4)
Figure13 shows the flow rate curve of hydraulic cylinder without rod chamber in the connection device. The flow of the first and the third cylinders vary during 2.88 s to 3.01 s. The flow of the first and the third cylinder decreases first and then increases. The flow of the second cylinder and the fourth cylinder varies greatly and becomes unstable during 2.88 s to 3.01 s. It is explained that pressure shock is the main cause of the flow change in the rodless chamber.(5)
Figure14 shows the changing displacement curve of four balancing cylinders in the hydraulic connecting device. Because the load of the first cylinder and the fourth cylinder is larger during 0 s to 3 s, the cylinder produces positive movement and the hydraulic oil discharges. The piston displacements of the four cylinders are 10 mm, −10 mm, −18 mm, and 20 mm, respectively. When the load is changed suddenly during 3 s to 6 s, the load of the second cylinder is the largest and the load of the first cylinder is the smallest. Therefore, the piston of the fourth cylinder produces the maximum displacement of 26 mm. The displacement of the third and fourth cylinders is 10 mm and −10 mm, and the displacement of the first cylinder is −26 mm.Figure 10
Input curve of signal source load.Figure 11
Pressure of four cylinders without rod chamber.Figure 12
Pressure variation curves of each hydraulic cylinder without rod chamber in the connection device.
(a)
(b)Figure 13
Flow rate curve of the hydraulic cylinder without rod chamber in the connection device.
(a)
(b)Figure 14
Displacement curve of the cylinder piston.Comparing with the curve of signal source load in Figure10, when the load changes drastically during 0–0.2 s and 2.8–3.4 s, it will cause a greater pressure impact to the hydraulic connecting device. If the loads of the four cylinders are obviously different, the pressure of the four cylinders are adjusted by connecting pipelines to ensure the same internal pressure of the rodless chamber, which is shown in Figure 12.The dynamic characteristics of the hydraulic balancing device show that it plays an important role of balancing oil pressure, wire tension, and load to a certain extent. It seriously affects the accurate monitoring of wire rope load which is affected by the load changing, the friction between piston and hydraulic, and the pressure loss caused by hydraulic flow.


## 4. Pressure and Friction Compensation of Hydraulic Connection Device

### 4.1. Pressure Loss

The viscous fluid flowing in the pipeline will be resisted and the energy will be lost due to liquid inductance, resistance, and capacitance of viscous fluid. The loss mainly includes pressure lost along the pipeline and local pressure loss [20]. The pressure lost along the pipeline refers to the pressure loss caused by the viscous force during fluid flowing through the straight pipe; the local pressure loss refers to the pressure loss caused by the sudden diameter change or bending of the pipe.The pressure lost along the pipeline can be described as follows:(12)Δpf=λldρv22,where λ represents the pressure coefficient along the pipeline, l means the length of the pipe, d means the inner diameter of the pipe, ρ denotes the liquid density, and v represents the average velocity of the liquid.The local pressure loss can be described as follows:(13)Δpr=ξρv22,where ξ represents the local resistance coefficient, which is related to the shape of pipe fittings and the Reynolds number Re.The total pressure loss can be expressed as follows:(14)Δp=Δpf+Δpr.


### 4.2. Friction Compensation Model

Sliding hysteresis friction force in the hydraulic cylinder is the main factor affecting the monitoring results [21]. Under the condition of tangential force, elastic deformation produces frictional force. When the force increases to a certain value, the sliding phenomenon appears. At the same time, it also shows viscous sliding, friction hysteresis, and presliding displacement, which are suitable for dynamic friction model. The Leuven friction model based on elastic bristle contact not only contains the friction characteristics of common LuGre friction model, but also uses hysteresis function with nonlocal memory to build more accurate model of each cylinder. The Leuven friction model is adopted for the hydraulic cylinder seal. The relationship between oil pressure and parameters in the Leuven friction model is fitted by the friction compensation test and the parameters of the Leuven friction model are estimated by curve fitting [22].The Leuven friction model [17] can be described as follows:(15)dzdt=v−σ0gvzv,f=σ0z+σ1dzdt+σ2v,gv=fc+fs−fc∗e−v/vs2,where v represents the relative velocity of the friction surface, z means the relative axial deformation between the sealing ring and the moving surface under viscous condition, σ0 denotes the axial stiffness coefficient of the sealing ring, σ1 represents the axial damping coefficient of the sealing ring, σ2 means the viscous friction coefficient of the system, fc represents the Coulomb friction, fs means the maximum static friction, vs denotes the critical speed, and gv describes the Stribeck Effect.When the system stabilityz = 0, the following equation can be deduced:(16)Ffsv=Fc+Fs−Fce−v/vs2sgnv+Kvv,where Kv means the viscous friction coefficient of the system.


#### 4.2.1. Friction Compensation Test

The test rig of friction compensation is shown in Figure15, including friction compensation test stand, oil supply device, and display screen. When the oil enters the rodless cavity through the oil supply device, the test is carried out.Figure 15
Friction test rig.The flow valves and other valves are equipped to control the flow rate and get the tested velocity of the piston. The pressure control valves adjust the pressure of outlet oil. When the adjustment is completed, the backpressure remains a constant.After adjusting the backpressure, the pressure and flow of oil are adjusted by the oil supply device. The oil pressure is set from 2 MPa to 12 MPa in order to avoid the zero drift and linearity of low oil pressure. The oil pressure and displacement of the tested cylinder and the balanced cylinder are recorded by LabVIEW software.


#### 4.2.2. Effect of Oil Pressure on Friction

When the piston of the balanced cylinder moves along the cylinder under oil pressure, friction resistance is produced. The higher the pressure is, the greater the resistance is. In Table1, the parameters of the Leuven friction model are obtained by adjusting the oil pressure.Table 1
Parameters of the Leuven friction model.
Oil pressure
Coulomb friction
Maximum static friction
Stribeck critical speed
Viscous friction coefficient
2
0.0799
0.1771
7.8386
0.0013
3
0.1095
0.1993
6.1813
0.0014
4
0.1331
0.2360
6.7047
0.0015
5
0.1557
0.2578
6.0063
0.0015
6
0.1813
0.2770
5.9152
0.0017
7
0.2116
0.2983
5.5787
0.0017
8
0.2368
0.3279
5.2612
0.0017
9
0.2584
0.3586
4.7855
0.0018
10
0.2963
0.3809
4.3099
0.0019
11
0.3356
0.4093
4.1943
0.0019
12
0.3192
0.4277
3.4387
0.0020Figures16–19 show the influence of pressure variation on maximum static friction, critical velocity, Coulomb friction, and viscous friction coefficient, respectively. The relationship between Fs, vs, Fc, Kv, and p can be described as equation (17) by MATLAB linear fitting. The friction compensation can be obtained by substituting equation (17) into equation (18):(17)Fc=0.0357+0.0254p,Fs=0.1276+0.0253p,vs=8.3503−0.3966p,Kv=0.001208+0.00006p,(18)Fv=Fc+Fs−Fce−v/vs2sgnv+Kvv.Figure 16
Effect of pressure change on the maximum static friction force.Figure 17
Effect of pressure change on the Stribeck critical speed.Figure 18
Effect of pressure change on the Coulomb friction.Figure 19
Effect of pressure change on the viscous friction coefficient.


## 4.1. Pressure Loss

The viscous fluid flowing in the pipeline will be resisted and the energy will be lost due to liquid inductance, resistance, and capacitance of viscous fluid. The loss mainly includes pressure lost along the pipeline and local pressure loss [20]. The pressure lost along the pipeline refers to the pressure loss caused by the viscous force during fluid flowing through the straight pipe; the local pressure loss refers to the pressure loss caused by the sudden diameter change or bending of the pipe.The pressure lost along the pipeline can be described as follows:(12)Δpf=λldρv22,where λ represents the pressure coefficient along the pipeline, l means the length of the pipe, d means the inner diameter of the pipe, ρ denotes the liquid density, and v represents the average velocity of the liquid.The local pressure loss can be described as follows:(13)Δpr=ξρv22,where ξ represents the local resistance coefficient, which is related to the shape of pipe fittings and the Reynolds number Re.The total pressure loss can be expressed as follows:(14)Δp=Δpf+Δpr.


## 4.2. Friction Compensation Model

Sliding hysteresis friction force in the hydraulic cylinder is the main factor affecting the monitoring results [21]. Under the condition of tangential force, elastic deformation produces frictional force. When the force increases to a certain value, the sliding phenomenon appears. At the same time, it also shows viscous sliding, friction hysteresis, and presliding displacement, which are suitable for dynamic friction model. The Leuven friction model based on elastic bristle contact not only contains the friction characteristics of common LuGre friction model, but also uses hysteresis function with nonlocal memory to build more accurate model of each cylinder. The Leuven friction model is adopted for the hydraulic cylinder seal. The relationship between oil pressure and parameters in the Leuven friction model is fitted by the friction compensation test and the parameters of the Leuven friction model are estimated by curve fitting [22].The Leuven friction model [17] can be described as follows:(15)dzdt=v−σ0gvzv,f=σ0z+σ1dzdt+σ2v,gv=fc+fs−fc∗e−v/vs2,where v represents the relative velocity of the friction surface, z means the relative axial deformation between the sealing ring and the moving surface under viscous condition, σ0 denotes the axial stiffness coefficient of the sealing ring, σ1 represents the axial damping coefficient of the sealing ring, σ2 means the viscous friction coefficient of the system, fc represents the Coulomb friction, fs means the maximum static friction, vs denotes the critical speed, and gv describes the Stribeck Effect.When the system stabilityz = 0, the following equation can be deduced:(16)Ffsv=Fc+Fs−Fce−v/vs2sgnv+Kvv,where Kv means the viscous friction coefficient of the system.


### 4.2.1. Friction Compensation Test

The test rig of friction compensation is shown in Figure15, including friction compensation test stand, oil supply device, and display screen. When the oil enters the rodless cavity through the oil supply device, the test is carried out.Figure 15
Friction test rig.The flow valves and other valves are equipped to control the flow rate and get the tested velocity of the piston. The pressure control valves adjust the pressure of outlet oil. When the adjustment is completed, the backpressure remains a constant.After adjusting the backpressure, the pressure and flow of oil are adjusted by the oil supply device. The oil pressure is set from 2 MPa to 12 MPa in order to avoid the zero drift and linearity of low oil pressure. The oil pressure and displacement of the tested cylinder and the balanced cylinder are recorded by LabVIEW software.


### 4.2.2. Effect of Oil Pressure on Friction

When the piston of the balanced cylinder moves along the cylinder under oil pressure, friction resistance is produced. The higher the pressure is, the greater the resistance is. In Table1, the parameters of the Leuven friction model are obtained by adjusting the oil pressure.Table 1
Parameters of the Leuven friction model.
Oil pressure
Coulomb friction
Maximum static friction
Stribeck critical speed
Viscous friction coefficient
2
0.0799
0.1771
7.8386
0.0013
3
0.1095
0.1993
6.1813
0.0014
4
0.1331
0.2360
6.7047
0.0015
5
0.1557
0.2578
6.0063
0.0015
6
0.1813
0.2770
5.9152
0.0017
7
0.2116
0.2983
5.5787
0.0017
8
0.2368
0.3279
5.2612
0.0017
9
0.2584
0.3586
4.7855
0.0018
10
0.2963
0.3809
4.3099
0.0019
11
0.3356
0.4093
4.1943
0.0019
12
0.3192
0.4277
3.4387
0.0020Figures16–19 show the influence of pressure variation on maximum static friction, critical velocity, Coulomb friction, and viscous friction coefficient, respectively. The relationship between Fs, vs, Fc, Kv, and p can be described as equation (17) by MATLAB linear fitting. The friction compensation can be obtained by substituting equation (17) into equation (18):(17)Fc=0.0357+0.0254p,Fs=0.1276+0.0253p,vs=8.3503−0.3966p,Kv=0.001208+0.00006p,(18)Fv=Fc+Fs−Fce−v/vs2sgnv+Kvv.Figure 16
Effect of pressure change on the maximum static friction force.Figure 17
Effect of pressure change on the Stribeck critical speed.Figure 18
Effect of pressure change on the Coulomb friction.Figure 19
Effect of pressure change on the viscous friction coefficient.


## 4.2.1. Friction Compensation Test

The test rig of friction compensation is shown in Figure15, including friction compensation test stand, oil supply device, and display screen. When the oil enters the rodless cavity through the oil supply device, the test is carried out.Figure 15
Friction test rig.The flow valves and other valves are equipped to control the flow rate and get the tested velocity of the piston. The pressure control valves adjust the pressure of outlet oil. When the adjustment is completed, the backpressure remains a constant.After adjusting the backpressure, the pressure and flow of oil are adjusted by the oil supply device. The oil pressure is set from 2 MPa to 12 MPa in order to avoid the zero drift and linearity of low oil pressure. The oil pressure and displacement of the tested cylinder and the balanced cylinder are recorded by LabVIEW software.


## 4.2.2. Effect of Oil Pressure on Friction

When the piston of the balanced cylinder moves along the cylinder under oil pressure, friction resistance is produced. The higher the pressure is, the greater the resistance is. In Table1, the parameters of the Leuven friction model are obtained by adjusting the oil pressure.Table 1
Parameters of the Leuven friction model.
Oil pressure
Coulomb friction
Maximum static friction
Stribeck critical speed
Viscous friction coefficient
2
0.0799
0.1771
7.8386
0.0013
3
0.1095
0.1993
6.1813
0.0014
4
0.1331
0.2360
6.7047
0.0015
5
0.1557
0.2578
6.0063
0.0015
6
0.1813
0.2770
5.9152
0.0017
7
0.2116
0.2983
5.5787
0.0017
8
0.2368
0.3279
5.2612
0.0017
9
0.2584
0.3586
4.7855
0.0018
10
0.2963
0.3809
4.3099
0.0019
11
0.3356
0.4093
4.1943
0.0019
12
0.3192
0.4277
3.4387
0.0020Figures16–19 show the influence of pressure variation on maximum static friction, critical velocity, Coulomb friction, and viscous friction coefficient, respectively. The relationship between Fs, vs, Fc, Kv, and p can be described as equation (17) by MATLAB linear fitting. The friction compensation can be obtained by substituting equation (17) into equation (18):(17)Fc=0.0357+0.0254p,Fs=0.1276+0.0253p,vs=8.3503−0.3966p,Kv=0.001208+0.00006p,(18)Fv=Fc+Fs−Fce−v/vs2sgnv+Kvv.Figure 16
Effect of pressure change on the maximum static friction force.Figure 17
Effect of pressure change on the Stribeck critical speed.Figure 18
Effect of pressure change on the Coulomb friction.Figure 19
Effect of pressure change on the viscous friction coefficient.


## 5. Field Test of Wire Rope Tension and Load Measurement under Compensation

### 5.1. Monitoring System and Compensation for Wire Rope Tension and Load

In Figure20, it can be seen that the monitoring system for wire rope tension and load is mainly composed of signal detection, signal transmission, signal acceptance, signal processing, and monitoring computer. Collected signals are processed and analyzed by the LabVIEW software in the monitoring computer. When the hoist is overloaded, the monitoring computer will give sound and light warnings; if the tension of four wire ropes is unbalanced, it will be compensated according to the Leuven friction model, and the compensation scheme is shown in Figure 21. After compensation, the load of the wire rope can be obtained, which is approximately equal to the sum tension of four wire ropes [23].Figure 20
Monitoring system structure of wire rope tension and load.Figure 21
Compensation scheme for wire rope tension and load.


### 5.2. Field Test Results of Wire Rope Tension and Load

In order to test the accuracy of measuring the tension and load of wire rope, a field test was carried out in a mine. In Figure22, it is shown that the hydraulic connecting device is installed in the field. The depth of the mine is 620 mm, the mass of the cage is 8.2 t, the number of wire ropes is four, the number of the tail rope is two, and the weight of the tail rope is 6.2 kg per meter. The data before and after compensation with the Leuven friction model are shown in Table 2. The total load of the hoist is approximately equal to the sum of the tensions of four wire ropes.Figure 22
The diagrammatic sketch of the on-site installation of oil pressure sensor. 1, oil pressure sensor; 2, connecting pipe; 3, connector; 4, globe valve.Table 2
Test data.
Position of hoist
Length of counterweight tail rope (m)
Measured value of sensor nos. 1, 2, 3, and 4 (kN)
Sum tension of four wire ropes (kN)
Total mass of hoist (t)
Mass of counterweight tail rope (t)
Before
After
Before
After
Pithead
620
34.7, 35.1, 35.8, 36.2
37.8, 39.6, 39.5, 38.7
141.8
155.6
15.888
7.688
Middle of the pit
300
29.6, 26.8, 28.3, 26.5
29.7, 30.6, 29.3, 29.1
111.2
118.7
11.92
3.72
Pit bottom
20
16.8, 17.7, 16.9, 16.7
21.1, 20, 20.4, 21.6
68.1
83.1
8.448
0.248It can be seen from the table that the tension at pithead before and after compensation is 145.2 kN and 155.6 kN, respectively, and the compensation rate reaches 9.7%.


## 5.1. Monitoring System and Compensation for Wire Rope Tension and Load

In Figure20, it can be seen that the monitoring system for wire rope tension and load is mainly composed of signal detection, signal transmission, signal acceptance, signal processing, and monitoring computer. Collected signals are processed and analyzed by the LabVIEW software in the monitoring computer. When the hoist is overloaded, the monitoring computer will give sound and light warnings; if the tension of four wire ropes is unbalanced, it will be compensated according to the Leuven friction model, and the compensation scheme is shown in Figure 21. After compensation, the load of the wire rope can be obtained, which is approximately equal to the sum tension of four wire ropes [23].Figure 20
Monitoring system structure of wire rope tension and load.Figure 21
Compensation scheme for wire rope tension and load.


## 5.2. Field Test Results of Wire Rope Tension and Load

In order to test the accuracy of measuring the tension and load of wire rope, a field test was carried out in a mine. In Figure22, it is shown that the hydraulic connecting device is installed in the field. The depth of the mine is 620 mm, the mass of the cage is 8.2 t, the number of wire ropes is four, the number of the tail rope is two, and the weight of the tail rope is 6.2 kg per meter. The data before and after compensation with the Leuven friction model are shown in Table 2. The total load of the hoist is approximately equal to the sum of the tensions of four wire ropes.Figure 22
The diagrammatic sketch of the on-site installation of oil pressure sensor. 1, oil pressure sensor; 2, connecting pipe; 3, connector; 4, globe valve.Table 2
Test data.
Position of hoist
Length of counterweight tail rope (m)
Measured value of sensor nos. 1, 2, 3, and 4 (kN)
Sum tension of four wire ropes (kN)
Total mass of hoist (t)
Mass of counterweight tail rope (t)
Before
After
Before
After
Pithead
620
34.7, 35.1, 35.8, 36.2
37.8, 39.6, 39.5, 38.7
141.8
155.6
15.888
7.688
Middle of the pit
300
29.6, 26.8, 28.3, 26.5
29.7, 30.6, 29.3, 29.1
111.2
118.7
11.92
3.72
Pit bottom
20
16.8, 17.7, 16.9, 16.7
21.1, 20, 20.4, 21.6
68.1
83.1
8.448
0.248It can be seen from the table that the tension at pithead before and after compensation is 145.2 kN and 155.6 kN, respectively, and the compensation rate reaches 9.7%.


## 6. Conclusion

Tension and load results measured by oil pressure sensor show that the method can avoid the violent fluctuation of measurement signals of wire rope, but the measurement results are inaccurate due to the loss of oil pressure in the hydraulic connecting device and the influence of friction force of piston on the cylinder wall.In this paper, to analyze the impact of friction and pressure loss, the wire rope with the hydraulic connecting device can be regarded as a spring-damper system without mass and the mathematical model is established. The dynamic characteristics of hydraulic cylinder under different pressure and flow rate, the influence of the connecting device on the pressure, and flow rate and speed caused by the load change and pressure impact are analyzed by using AMESim to establish the model and make simulation of the single hydraulic system and hydraulic connection device. The relevant parameters of the Leuven friction model and compensation scheme are obtained by the friction compensation test. The test of the monitoring system and compensation for wire rope tension and load are carried out. The results show that the compensation based on the Leuven friction model improves the accuracy of wire rope tension and load monitoring, which is of great significance for ensuring the safety of the coal mine hoisting system.



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*Source: 3809242-2019-05-16.xml*