Electro-hydraulic hybrid transmission system experiment table and simulation experiment method thereof

Abstract

The invention discloses an electro-hydraulic hybrid transmission system experiment table and a simulation experiment method thereof, the electro-hydraulic hybrid transmission system experiment table comprises two electro-hydraulic hybrid simulation units for simulating two cutting parts of a coal mining machine, the two electro-hydraulic hybrid simulation units are respectively provided with a motor and a hydraulic motor for inputting torque, and a load simulation device connected with an output torque, load output by the load simulation device is that current of the motors changes, so that operation of the hydraulic motors is controlled, and two one-way hydraulic one-way compensation oil pipes are arranged between two hydraulic loops of the two hydraulic motors, so that hydraulic oil complementation can be achieved between the two hydraulic loops. Three modes, namely a pure motor working mode experiment, an electro-hydraulic hybrid transmission single-pump single-side working mode experiment and an electro-hydraulic hybrid transmission double-pump double-side combined working mode, of the cutting part of the coal mining machine can be simulated, the feasibility of a structure scheme and a control method is verified through the mode experiments, and the practical difficulty of the design experiment of the cutting part of the coal mining machine is solved.

Description

Technical Field

[0001] The invention relates to the technical field of transmission of a cutting part of a coal mining machine, and in particular to an electric-hydraulic hybrid transmission system test bench and a simulation experiment method thereof. Background Art

[0002] With the development of my country's economy and the increase in demand for energy, the amount of coal mined is large and the mining time is long, and mining equipment often suffers from insufficient power. Therefore, large-scale and high-power coal equipment has become the main development trend of the coal mining machine market; due to the uneven thickness of coal seams across the country and complex geological conditions, cutting under complex coal seams may encounter sudden changes in coal seam hardness or coal rock distribution, resulting in coal mining machine cutting with large load fluctuation range, high load and imbalance; in addition, the left and right cutting drums of the coal mining machine work in different upper and lower positions, resulting in uneven cutting load on the left and right sides.

[0003] However, due to the space limitations of the coal mining machine and the coal seam, the coal mining machine cannot be equipped with a high-power flameproof inverter, and the cutting part cannot adjust the torque. In response to the above problems, the traditional coal mining machine solution is to design the corresponding roller and transformer according to the geological conditions of the working face provided by the user, so as to basically determine the cutting speed and maximum power, and adopt the maximum power demand design. The working faces with different geological conditions need to re-adapt the cutting roller, and select the coal mining machine model according to the maximum power demand.

[0004] The new problem that arises is that due to the limitations of the space for coal mining machines and coal seams, the size of the transformer has an upper limit, and the heat generation caused by the transformer increasing the power means that there is an upper limit to the power increase. In addition, the maximum power design and the inability to adjust the power result in serious energy waste.

[0005] The traditional coal mining machine cutting part uses a three-phase asynchronous motor as the power source, and the coal mining machine cutting rocker arm uses a hydraulic pump station as the power source. When the coal mining machine is mining on the working face, the pump station is first adjusted to work to raise or lower the rocker arm to the target height and then locked. The pump station is idle and waiting, and the cutting motor works again for cutting and mining. There is no cutting when it is raised, and the pump station is only idle and does not work when cutting. Therefore, there is a waste of energy when the pump station is raised, and this part of the energy can be used in the cutting part. In addition, preliminary research shows that adjusting the traction speed and cutting torque according to the changes in coal and rock characteristics can better meet production needs.

[0006] Due to the high power of coal mining equipment, direct experimental operation is very dangerous; the cost is high, and the experiment requires the removal of the rocker arm shell, resulting in great economic losses; the large size makes it difficult to move, requiring a larger test site, and the poor environmental conditions underground make experiments inconvenient and the implementation of the plan difficult.

[0007] Based on this starting point, three asynchronous motors are used as the main power source and the hydraulic pump station is used as the auxiliary power source. A test bench that can simulate the cutting of the coal mining machine and can simulate the electro-hydraulic hybrid transmission is proposed. The technical route of providing adjustable torque with electro-hydraulic hybrid transmission solves practical needs, tests the cutting characteristics of the coal mining machine and the mechanical coupling characteristics of the hybrid transmission system, verifies the feasibility of the structural scheme and control method, and at the same time, the test bench with easy-to-modify structure, safety and reliability, and convenient experiments has a strong practical significance for solving the practical difficulties in the design experiment of the cutting part of the coal mining machine. Summary of the invention

[0008] In view of the above problems, the present invention provides an electro-hydraulic hybrid transmission system test bench, which can simulate three modes of operation of two cutting parts. The specific scheme is as follows: An electro-hydraulic hybrid transmission system test bench comprises a first electro-hydraulic hybrid simulation unit and a second electro-hydraulic hybrid simulation unit for simulating two cutting parts of a coal mining machine. The first electro-hydraulic hybrid simulation unit includes a first motor for inputting torque, a first hydraulic motor and a first load simulation device for applying a load to the output torque, wherein the first load simulation device applies a load to the output torque to change the current in the first motor, and a first current sensor for detecting the current value is installed on the first motor; The second electro-hydraulic hybrid simulation unit includes a second motor for inputting torque, a second hydraulic motor and a second load simulation device for applying a load to the output torque, wherein the second load simulation device applies a load to the output torque to change the current in the second motor, and a second current sensor for detecting the current value is installed on the second motor; The first hydraulic circuit in the first electro-hydraulic hybrid simulation unit comprises a first hydraulic pump station connected to the oil inlet of the first hydraulic motor and an oil cylinder connected to the oil discharge port of the first hydraulic motor, wherein the oil cylinder is connected to the first hydraulic pump station; The second hydraulic circuit in the second electric-hydraulic hybrid simulation unit includes a second hydraulic pump station connected to the oil inlet of the second hydraulic motor and an oil cylinder connected to the oil discharge port of the second hydraulic motor, wherein the oil cylinder is connected to the second hydraulic pump station; A first oil pipeline is connected between the first hydraulic pump station and the first hydraulic motor, a second oil pipeline is connected between the second hydraulic pump station and the second hydraulic motor, and a first one-way compensation oil pipeline capable of transporting hydraulic oil in the first oil pipeline to the second oil pipeline and a second one-way compensation oil pipeline capable of transporting hydraulic oil in the second oil pipeline to the first oil pipeline are respectively connected between the first oil pipeline and the second oil pipeline; A first electromagnetic proportional valve is provided in the first one-way compensation oil pipe, and a second electromagnetic proportional valve is provided in the second one-way compensation oil pipe; When the current value detected by the first current sensor increases, the opening of the second electromagnetic proportional valve increases proportionally, or when the current value detected by the second current sensor increases, the opening of the first electromagnetic proportional valve increases proportionally.

[0009] Furthermore, the first electro-hydraulic hybrid simulation unit further includes a first torque coupler, the first motor and the first hydraulic motor are respectively connected to the first torque coupler so that the respective input power is coupled in parallel, and the torque is output through the first output shaft of the first torque coupler, and the first output shaft is connected to the first load simulation device; The first torque coupler includes two input shafts, namely a first input shaft and a second input shaft, the first input shaft is connected to the first output shaft through a first gear set, and the first input shaft is connected to the first motor, the second input shaft is connected to the first input shaft through a second gear set, the second input shaft is connected to the first hydraulic motor, and a first one-way clutch is provided between the second input shaft and the first hydraulic motor; The second electric-hydraulic hybrid simulation unit further includes a second torque coupler, the second motor and the second hydraulic motor are respectively connected to the second torque coupler so that the respective input power is coupled in parallel, and the torque is output through the second output shaft of the second torque coupler, and the second output shaft is connected to the second load simulation device; The second torque coupler includes two input shafts, namely a third input shaft and a fourth input shaft. The third input shaft is transmission-connected to the second output shaft via a third gear set, and the third input shaft is connected to the second motor; the fourth input shaft is transmission-connected to the third input shaft via a fourth gear set, the fourth input shaft is connected to the second hydraulic motor, and a second one-way clutch is arranged between the fourth input shaft and the second hydraulic motor.

[0010] Furthermore, the first motor and the second motor are both three-phase asynchronous motors.

[0011] Furthermore, the first load simulation device and the second load simulation device are both magnetic powder brakes.

[0012] Furthermore, a first torque and speed sensor is connected between the first load simulation device and the first output shaft; and a second torque and speed sensor is connected between the second load simulation device and the second output shaft.

[0013] Further, a first electromagnetic proportional reversing valve is provided in the first hydraulic circuit, a P port of the first electromagnetic proportional reversing valve is connected to an oil outlet of the first hydraulic pump station, a A port of the first electromagnetic proportional reversing valve is connected to the first oil delivery pipe, an oil discharge port of the first hydraulic motor is connected to a B port of the first electromagnetic proportional reversing valve, and a T port of the first electromagnetic proportional reversing valve is connected to an oil cylinder; A second electromagnetic proportional reversing valve is provided in the second hydraulic circuit, the P port of the second electromagnetic proportional reversing valve is connected to the oil outlet of the second hydraulic pump station, the A port of the second electromagnetic proportional reversing valve is connected to the second oil delivery pipe, the oil discharge port of the second hydraulic motor is connected to the B port of the second electromagnetic proportional reversing valve, and the T port of the second electromagnetic proportional reversing valve is connected to the oil cylinder; A first high-pressure relief valve is connected in parallel at both ends of the first hydraulic pump station; A second high-pressure relief valve is connected in parallel at both ends of the second hydraulic pump station; The T port of the first electromagnetic proportional reversing valve and the T port of the second electromagnetic proportional reversing valve are both connected to the low-pressure relief valve, and the low-pressure relief valve is connected to the oil cylinder.

[0014] Furthermore, the first electromagnetic proportional reversing valve and the second electromagnetic proportional reversing valve both have a Y-type neutral position function.

[0015] Further, when the current value of the first motor exceeds the set upper limit value, the first electromagnetic proportional reversing valve opens, and its opening increases proportionally with the increase of the current value; when the current value of the second motor exceeds the set upper limit value, the second electromagnetic proportional reversing valve opens, and its opening increases proportionally with the increase of the current value.

[0016] Furthermore, it also includes an industrial computer, which is electrically connected to the first hydraulic pump station, the first motor, the first load simulation device, the first electromagnetic proportional reversing valve, the first electromagnetic proportional valve, the first torque and speed sensor, the first current sensor, the second hydraulic pump station, the second motor, the second load simulation device, the second electromagnetic proportional reversing valve, the second electromagnetic proportional valve, the second torque and speed sensor, and the second current sensor.

[0017] Furthermore, a simulation experiment method of an electro-hydraulic hybrid transmission system test bench has the following specific steps: S1, pure motor working mode experiment: a. The industrial computer controls the first motor and the first hydraulic pump station to start. The first motor drives the first input shaft to rotate, and the first motor outputs the first input shaft after being decelerated by the first gear set. The first load simulation device applies a load to the first output shaft, and detects the actual output torque and actual speed of the first output shaft through the first torque and speed sensor. At this time, the first electromagnetic proportional reversing valve is in a closed state, and the first hydraulic motor does not output power to the outside; b. At the same time, the industrial computer controls the second motor and the second hydraulic pump station to start, the second motor drives the third input shaft to rotate, and the third gear group decelerates the third input shaft and outputs the third input shaft. The second load simulation device applies a load to the second output shaft, and the second torque and speed sensor detects the actual output torque and actual speed of the second output shaft. At this time, the second electromagnetic proportional reversing valve is in a closed state, and the second hydraulic motor does not output power to the outside; S2, electro-hydraulic hybrid transmission single pump single side working mode experiment: c. The industrial computer controls the first motor and the first hydraulic motor to start at the same time. The first motor drives the first input shaft to rotate, and the first motor outputs the first input shaft after being decelerated by the first gear set. The first load simulation device applies a load to the first output shaft, and detects the actual output torque and actual speed of the first output shaft through the first torque and speed sensor. The first motor current upper limit value is set by load adjustment of the first load simulation device. As the load of the first load simulation device increases, the current of the first motor will increase accordingly. When the current value of the first motor read by the first current sensor exceeds the upper limit value, the first electromagnetic proportional reversing valve opens, the first hydraulic pump station supplies oil to the first hydraulic motor, and the first hydraulic motor starts to work. After the first hydraulic motor is locked with the first one-way clutch, the auxiliary power is input to the first torque coupler through the second input shaft; d, or the industrial computer controls the second motor and the second hydraulic motor to start at the same time, the second motor drives the third input shaft to rotate, and the second motor is output through the first output shaft after being decelerated by the second gear set, the second load simulation device applies a load to the second output shaft, and detects the actual output torque and actual speed of the second output shaft through the second torque and speed sensor, and sets the upper limit value of the second motor current by load adjustment of the second load simulation device. As the load of the second load simulation device increases, the current of the second motor will increase accordingly. When the current value of the second motor read by the second current sensor exceeds the upper limit value, the second electromagnetic proportional reversing valve opens, the second hydraulic pump station supplies oil to the second hydraulic motor, and the second hydraulic motor starts to work. After the second hydraulic motor is locked with the second one-way clutch, the auxiliary power is input to the second torque coupler through the fourth input shaft; S3, Electro-hydraulic hybrid transmission dual-pump dual-side joint working mode experiment: e. The industrial computer controls the first motor and the first hydraulic pump station to start. The first motor drives the first input shaft to rotate, and the first motor outputs the first input shaft after being decelerated by the first gear set. The first load simulation device applies a load to the first output shaft, and detects the actual output torque and actual speed of the first output shaft through the first torque and speed sensor. At this time, the first electromagnetic proportional reversing valve is in a closed state, and the first hydraulic motor does not output power to the outside. The first load simulation device performs load adjustment and sets the upper limit value of the first motor current. As the load of the first load simulation device increases, the current of the first motor will increase accordingly. When the current value of the first motor read by the first current sensor exceeds the upper limit value, the first electromagnetic proportional reversing valve opens, and the first hydraulic pump station supplies oil to the first hydraulic motor. The first hydraulic motor starts to work. After the first hydraulic motor is locked with the first one-way clutch, the auxiliary power is input to the first torque coupler through the second input shaft; f. At the same time, the industrial computer controls the second motor and the second hydraulic pump station to start, the second motor drives the third input shaft to rotate, and the output is output through the second output shaft after being decelerated by the third gear set. The second load simulation device applies a load to the second output shaft, and detects the actual output torque and actual speed of the second output shaft through the second torque and speed sensor. At this time, the second electromagnetic proportional reversing valve is in a closed state, and the second hydraulic motor does not output power to the outside. The second load simulation device performs load adjustment and sets the upper limit value of the second motor current. As the load of the second load simulation device increases, the current of the second motor will increase accordingly. When the second current sensor reads that the current value of the second motor exceeds the upper limit value, the second electromagnetic proportional reversing valve opens, and the second hydraulic pump station supplies oil to the second hydraulic motor, and the second hydraulic motor starts to work. After the second hydraulic motor is locked with the second one-way clutch, the auxiliary power is input to the second torque coupler through the fourth input shaft; g. When the opening of the first electromagnetic proportional reversing valve reaches the maximum, the power of the first hydraulic motor reaches the upper limit, and the output torque of the first output shaft still cannot match the load of the first load simulation device, the second electromagnetic proportional reversing valve continues to open under the condition that the power demand of the second output shaft is met. At the same time, the industrial computer controls the second electromagnetic proportional valve to open, so that the second hydraulic pump station inputs the surplus hydraulic oil into the first hydraulic circuit through the second one-way compensation oil pipe, so that the auxiliary power of the first hydraulic motor is further improved, so that the first output shaft can match the load of the first load simulation device; h, or when the opening of the second electromagnetic proportional reversing valve reaches the maximum, the power of the second hydraulic motor reaches the upper limit, and the output torque of the second output shaft still cannot match the load of the second load simulation device, the first hydraulic motor continues to open the first electromagnetic proportional reversing valve under the condition of meeting the power requirement of the first output shaft. At the same time, the industrial computer controls the opening of the first electromagnetic proportional valve, so that the first hydraulic pump station inputs the surplus hydraulic oil into the second hydraulic circuit through the first one-way compensation oil pipe, so that the auxiliary power of the second hydraulic motor is further enhanced, so that the second output shaft can match the load of the second load simulation device.

[0018] Compared with the prior art, the advantages of the present invention are as follows: 1. The present invention can simulate three modes of the cutting part of the coal mining machine by designing the test bench of the above structure: pure motor working mode experiment, electro-hydraulic hybrid transmission single pump single-side working mode experiment and electro-hydraulic hybrid transmission double pump double-side joint working mode, and verify the feasibility of the structural scheme and control method through mode experiments to solve the practical difficulties in the design experiment of the cutting part of the coal mining machine; 2. The invention takes into account the existing dual height adjustment pump station on the existing coal mining machine, and uses it as the auxiliary power source of this experimental platform, designs a torque-coupled coal mining machine cutting part electro-hydraulic hybrid transmission system, fully utilizes the existing hydraulic power of the coal mining machine, saves layout space, and further couples the power of the coal mining machine height adjustment pump station with the cutting motor to provide sufficient auxiliary power for the coal mining machine cutting part under different working conditions. It can effectively solve the problem that the cutting torque of the coal mining machine cannot be adjusted with load fluctuations, and provide greater cutting power to cope with high-load conditions. It fully utilizes the output characteristics of the dual power source, timely supplements the kinetic energy of the coal mining machine drum, avoids the problem of overload and stall of the coal mining machine cutting motor, and reduces the risk of cutting motor failure; 3. The present invention uses a torque coupling mechanism to complete the torque coupling between power sources, which can give full play to the torque-increasing effect of the auxiliary power source and achieve the goal of optimal distribution of the comprehensive torque of the coal mining and cutting part. The torque coupling device can avoid the problem of difficult installation due to narrow space, reduce the difficulty of processing and installation, and achieve the purpose of maximizing cutting efficiency and optimizing the comprehensive performance of coal mining; 4. The present invention can form a pressure difference between the inlet and outlet of the hydraulic motor by connecting high-pressure relief valves in parallel at both ends of the hydraulic pump station and setting a low-pressure relief valve in the oil unloading pipeline between the electromagnetic proportional reversing valve and the cylinder, thereby providing a guarantee for the power demand of the hydraulic motor.

[0019] 5. The present invention reads the input current value of the motor in the electro-hydraulic hybrid and the torque value of the output shaft through the upper computer, controls the opening of the electromagnetic proportional reversing valve and the proportional reversing valve according to the change of the input current value, and controls the input power of the hydraulic motor, so as to study the dynamic characteristics of coal mining machine cutting, including experimental simulation of the cutting dynamic characteristics of traditional coal mining machines with pure electric motors and the hybrid cutting dynamic characteristics of hybrids, and records the experimental data in time to provide support for the conclusion summary after the test. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 This is a layout diagram of the test bench of the electric-hydraulic hybrid transmission system of the present invention; Figure 2 It is a hydraulic-mechanical principle diagram of the electric-hydraulic hybrid transmission system test bench of the present invention; Figure 3 This is a power principle diagram of the pure motor working mode of the present invention; Figure 4 This is a power principle diagram of the single-pump single-side working mode of the electro-hydraulic hybrid transmission of the present invention; Figure 5 This is the power principle diagram mode 1 of the electro-hydraulic hybrid transmission double-pump double-side joint working mode of the present invention; Figure 6 This is the power principle diagram mode 2 of the electro-hydraulic hybrid transmission double-pump double-side joint working mode of the present invention; Figure 7 It is a structural diagram of the electric-hydraulic hybrid of the present invention; Figure 8 It is a structural diagram of the assembly platform located at the bottom of the electric-hydraulic hybrid; Fig. 9 It is the structural diagram of the connection end of the one-way clutch; Reference numerals: 1-1, first motor; 1-2, second motor; 2-1, first coupling; 2-2, second coupling; 3-1, first torque coupler; 3-2, second torque coupler; 4-1, first torque and speed sensor; 4-2, second torque and speed sensor; 5-1. A first load simulation device; 5-2. A second load simulation device; 6. Assembly platform; 7-1, first hydraulic motor; 7-2, second hydraulic motor; 8-1, first one-way clutch; 8-2, second one-way clutch; 8-3, inner ring; 8-4, outer ring; 8-5, roller; 8-6, spring; 9. First high-pressure relief valve; 13. Second high-pressure relief valve; 14. Low-pressure relief valve; 10-1, first hydraulic pump station; 10-2, second hydraulic pump station; 11-1, first electromagnetic proportional valve; 11-2, second electromagnetic proportional valve; 12-1, first electromagnetic proportional reversing valve; 12-2, second electromagnetic proportional reversing valve; 15-1, first oil pipeline; 15-2, second oil pipeline; 16-1, first one-way compensation oil pipe; 16-2, second one-way compensation oil pipe; 17. Oil cylinder; 18-1, first input shaft; 18-2, second input shaft; 18-3, third input shaft; 18-4, fourth input shaft; 19-1, first output shaft; 19-2, second output shaft; 20. First slide groove; 21. Second slide groove; 22. Third slide groove; 23. Mounting hole; 24. Assembly platform. DETAILED DESCRIPTION

[0021] The technical solution of the invention will be described clearly and completely below. Obviously, the described embodiments are only part of the embodiments of the invention, rather than all of the embodiments.

[0022] Based on the embodiments of the invention, all other embodiments obtained by ordinary technicians in this field without making any creative work shall fall within the scope of protection of the invention.

[0023] In the description of the invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the invention and simplifying the description, rather than indicating or implying that the device or element referred to has a specific orientation, is constructed and operated in a specific orientation, and therefore cannot be understood as limiting the invention. In addition, the terms "first", "second", and "third" are used for descriptive purposes only, and cannot be understood as indicating or implying relative importance.

[0024] In the description of the invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the invention can be understood according to specific circumstances. Example 1

[0025] like Figure 1As shown, an electro-hydraulic hybrid transmission system test bench includes a first electro-hydraulic hybrid simulation unit and a second electro-hydraulic hybrid simulation unit for simulating two cutting parts of a coal mining machine.

[0026] The first electro-hydraulic hybrid simulation unit includes a first motor 1-1 for inputting torque, a first hydraulic motor 7-1 and a first load simulation device 5-1 for applying load to the output torque. The first load simulation device 5-1 applies load to the output torque. The first load simulation device 5-1 simulates the load generated by the coal seam on the lower left cutting part of the coal mining machine, thereby changing the current in the first motor 1-1. A first current sensor for detecting the current value is installed on the first motor 1-1.

[0027] The first load simulation device 5 - 1 is a magnetic powder brake, and a first torque and speed sensor 4 - 1 is connected between the first load simulation device 5 - 1 and the first output shaft 19 - 1 .

[0028] The first motor 1 - 1 is a three-phase asynchronous motor, and a first current sensor is connected to the first motor 1 - 1 .

[0029] Specifically, the first electro-hydraulic hybrid simulation unit further includes a first torque coupler 3-1, the first motor 1-1 and the first hydraulic motor 7-1 are respectively connected to the first torque coupler 3-1 so that the respective input power is coupled in parallel, and the torque is output through the first output shaft of the first torque coupler 3-1, and the first output shaft is connected to the first load simulation device 5-1; The first torque coupler 3-1 includes two input shafts, namely a first input shaft 18-1 and a second input shaft 18-2. The first input shaft 18-1 is connected to the first output shaft 19-1 through a first gear set, and the first input shaft 18-1 is connected to the first motor 1-1 through a first coupling 2-1. The second output shaft 19-2 is connected to the first input shaft 18-1 through a second gear set, and the second input shaft 18-2 is connected to the first hydraulic motor 7-1. A first one-way clutch 8-1 is provided between the second input shaft 18-2 and the first hydraulic motor 7-1.

[0030] The second electro-hydraulic hybrid simulation unit includes a second motor 1-2 for inputting torque, a second hydraulic motor 7-2 and a second load simulation device 5-2 for applying load to the output torque. The second load simulation device 5-2 applies load to the output torque. The second load simulation device 5-2 simulates the load generated by the coal seam on the upper right cutting part of the coal mining machine, thereby changing the current in the second motor 1-2. A second current sensor for detecting the current value is installed on the second motor 1-2.

[0031] The second load simulation device 5 - 2 is a magnetic powder brake, and a second torque and speed sensor 4 - 2 is connected between the second load simulation device 5 - 2 and the second output shaft 19 - 2.

[0032] The second motor 1 - 2 is a three-phase asynchronous motor, and a second current sensor is connected to the second motor 1 - 2 .

[0033] Specifically, the second electro-hydraulic hybrid simulation unit further includes a second torque coupler 3-2, the second motor 1-2 and the second hydraulic motor 7-2 are respectively connected to the second torque coupler 3-2 so that the respective input power is coupled in parallel, and the torque is output through the second output shaft of the second torque coupler 3-2, and the second output shaft is connected to the second load simulation device 5-2; The second torque coupler 3-2 includes two input shafts, namely the third input shaft 18-3 and the fourth input shaft 18-4. The third input shaft 18-3 is connected to the second output shaft 19-2 through the third gear set, and the third input shaft 18-3 is connected to the second motor 1-2 through the second coupling 2-2. The fourth input shaft 18-4 is connected to the third input shaft 18-3 through the fourth gear set, and the fourth input shaft 18-4 is connected to the second hydraulic motor 7-2. A second one-way clutch 8-2 ​​is provided between the fourth input shaft 18-4 and the second hydraulic motor 7-2. Example 2

[0034] like Figure 1 As shown, it also includes a first hydraulic circuit and a second hydraulic circuit.

[0035] The first hydraulic circuit in the first electro-hydraulic hybrid simulation unit includes a first hydraulic pump station 10-1 connected to the oil inlet of the first hydraulic motor 7-1, and a cylinder 17 connected to the oil discharge port of the first hydraulic motor 7-1, a first oil pipeline 15-1 is connected between the first hydraulic pump station 10-1 and the first hydraulic motor 7-1, and the cylinder 17 is connected to the first hydraulic pump station 10-1. Specifically, the first hydraulic circuit is provided with a first electromagnetic proportional reversing valve 12-1, the first electromagnetic proportional reversing valve 12-1 is a Y-type middle position function, the P port of the first electromagnetic proportional reversing valve 12-1 is connected to the oil outlet of the first hydraulic pump station 10-1, the A port of the first electromagnetic proportional reversing valve 12-1 is connected to the first oil pipeline 15-1, the oil discharge port of the first hydraulic motor 7-1 is connected to the B port of the first electromagnetic proportional reversing valve 12-1, and the T port of the first electromagnetic proportional reversing valve 12-1 is connected to the cylinder 17. When the current value of the first motor 1 - 1 exceeds the set upper limit value, the first electromagnetic proportional reversing valve 12 - 1 opens, and its opening increases proportionally with the increase of the current value.

[0036] The second hydraulic circuit in the second electro-hydraulic hybrid simulation unit includes a second hydraulic pump station 10-2 connected to the oil inlet of the second hydraulic motor 7-2, and a cylinder 17 connected to the oil discharge port of the second hydraulic motor 7-2, a second oil pipeline 15-2 is connected between the second hydraulic pump station 10-2 and the second hydraulic motor 7-2, and the cylinder 17 is connected to the second hydraulic pump station 10-2. Specifically, a second electromagnetic proportional reversing valve 12-2 is provided in the second hydraulic circuit, and the second electromagnetic proportional reversing valve 12-2 has a Y-type middle position function, the P port of the second electromagnetic proportional reversing valve 12-2 is connected to the oil outlet of the second hydraulic pump station 10-2, the A port of the second electromagnetic proportional reversing valve 12-2 is connected to the second oil pipeline 15-2, the oil discharge port of the second hydraulic motor 7-2 is connected to the B port of the second electromagnetic proportional reversing valve 12-2, and the T port of the second electromagnetic proportional reversing valve 12-2 is connected to the cylinder 17. When the current value of the second motor 1-2 exceeds the set upper limit value, the second electromagnetic proportional reversing valve 12-2 opens, and its opening increases proportionally with the increase of the current value.

[0037] A first one-way compensation oil pipe 16-1 capable of conveying hydraulic oil in the first oil pipe 15-1 to the second oil pipe 15-2 and a second one-way compensation oil pipe 16-2 capable of conveying hydraulic oil in the second oil pipe 15-2 to the first oil pipe 15-1 are respectively connected between the first oil pipe 15-1 and the second oil pipe 15-2. A first electromagnetic proportional valve 11-1 is arranged in the first one-way compensation oil pipe 16-1, and a second electromagnetic proportional valve 11-2 is arranged in the second one-way compensation oil pipe 16-2. When the current value on the first motor 1-1 increases, the opening of the second electromagnetic proportional valve 11-2 increases in proportion, or when the current value on the second motor 1-2 increases, the opening of the first electromagnetic proportional valve 11-1 increases in proportion. Example 3

[0038] The present invention provides a guarantee for the power demand of the hydraulic motor by respectively arranging a high-pressure relief valve and a low-pressure relief valve 14 at the inlet and outlet of the hydraulic motor so that there is a pressure difference between the inlet and outlet of the hydraulic motor. The specific scheme is as follows: like Figure 1 As shown, The first high-pressure relief valve 9 is connected in parallel at both ends of the first hydraulic pump station 10-1; A second high-pressure relief valve 13 is connected in parallel at both ends of the second hydraulic pump station 10-2; The T port of the first electromagnetic proportional reversing valve 12 - 1 and the T port of the second electromagnetic proportional reversing valve 12 - 2 are both connected to the low-pressure relief valve 14 , and the low-pressure relief valve 14 is connected to the oil cylinder 17 . Example 4

[0039] In order to facilitate the control of the electric-hydraulic hybrid operation and record the experimental data, the present invention has further improvements, the specific scheme is as follows: It also includes an industrial computer, which is electrically connected to the first hydraulic pump station 10-1, the first motor 1-1, the first load simulation device 5-1, the first electromagnetic proportional reversing valve 12-1, the first electromagnetic proportional valve 11-1, the first torque and speed sensor 4-1, the first current sensor, the second hydraulic pump station 10-2, the second motor 1-2, the second load simulation device 5-2, the second electromagnetic proportional reversing valve 12-2, the second electromagnetic proportional valve 11-2, the second torque and speed sensor 4-2 and the second current sensor. Example 5

[0040] In order to make the test bench modular, the present invention has the following improvements, and the specific scheme is as follows: like Figure 7 and Figure 8 As shown, the assembly platform 624 for the test bench has a first slide 20 in the middle of the assembly platform 624, and the first slide 20 is plugged with the torque coupler in the electric-hydraulic hybrid. A second slide 21 and a third slide 22 perpendicular to the first slide 20 are provided on one side of the first slide 20. The second slide 21 corresponds to the input shaft position of the torque coupler. A hydraulic motor is slidably connected in the second slide 21. The hydraulic motor slides in the second slide 21, and the distance between the hydraulic motor and the input shaft is adjusted to facilitate the installation or removal of the one-way clutch. The third slide 22 corresponds to the output shaft position of the torque coupler. A magnetic powder brake is slidably connected in the third slide 22. The magnetic powder brake slides in the third slide 22, and the distance between the magnetic powder brake and the output shaft is adjusted to facilitate the installation or removal of the torque rotation sensor. A mounting hole 23 is provided on the other side of the first slide 20, and the mounting hole 23 corresponds to the input shaft on the other side of the torque coupler. A motor is installed at the mounting hole 23. Example 6

[0041] The one-way clutch has the characteristic of one-way torque transmission, and its function is to realize the connection and separation between the hydraulic motor and the torque coupler. Figure 9 As shown, the one-way clutch is divided into an inner ring 8-3, an outer ring 8-4, a roller 8-5, and a spring 8-6. The outer ring 8-4 is connected and fixed to the input end of the torque coupler shaft, and the inner ring 8-3 is connected and fixed to the output shaft of the hydraulic motor. A plurality of evenly arranged right-angle cuts are provided along the circumference of the inner ring 8-3, and a spring 8-6 parallel to the horizontal cut is provided on the vertical cut surface of the right-angle cut, and the roller 8-5 is provided at the outer end of the spring 8-6.

[0042] When the inner ring 8-3 and the outer ring 8-4 rotate in opposite directions, Figure 9As shown in the left figure, roller 8-5 compresses spring 8-6 inward, the space becomes larger, and the inner and outer rings 8-4 are separated. At this time, the hydraulic motor does not drive the input shaft of the torque coupler to rotate.

[0043] When the direction of the hydraulic motor is consistent with that of its input shaft, but the speed of the hydraulic motor is lower than that of the input shaft, the roller 8-5 of the inner ring 8-3 moves outward due to the centrifugal force. However, due to insufficient speed, although the roller 8-5 is in contact with the outer ring 8-4, the friction force generated is insufficient to lock the roller 8-5 with the outer ring 8-4. Therefore, the hydraulic motor cannot drive the input shaft of the torque coupler to rotate: When the direction of the hydraulic motor is consistent with that of its input shaft and its speed is greater than that of the input shaft, the balls are subjected to sufficient centrifugal force to move outward, and the rollers 8-5 and the outer ring 8-4 are contacted and locked as a whole. At this time, the hydraulic motor drives the input shaft of the torque coupler to rotate.

[0044] From the above scheme, it can be seen that the hydraulic motor does not provide auxiliary torque to the output shaft instantaneously. It is because the increase in motor current causes the opening of the electromagnetic proportional reversing valve to continue to increase, so that the hydraulic motor receives the increased oil pressure and can lock with the input shaft to provide auxiliary power. Example 7

[0045] like Figures 2 to 5 As shown in the figure, the simulation experimental method of the electric-hydraulic hybrid transmission system test bench has the following specific steps: S1, pure motor working mode experiment: a. The industrial computer controls the first motor 1-1 and the first hydraulic pump station 10-1 to start. The first motor 1-1 drives the first input shaft 18-1 to rotate, and the first input shaft 18-1 is output through the first output shaft 19-1 after being decelerated by the first gear set. The first load simulation device 5-1 applies a load to the first output shaft 19-1, and detects the actual output torque and actual speed of the first output shaft 19-1 through the first torque and speed sensor 4-1. At this time, the first electromagnetic proportional reversing valve 12-1 is in a closed state, and the first hydraulic motor 7-1 does not output power to the outside; b. At the same time, the industrial computer controls the second motor 1-2 and the second hydraulic pump station 10-2 to start, the second motor 1-2 drives the third input shaft 18-3 to rotate, and the third gear group decelerates and outputs the third input shaft 18-3 through the second output shaft 19-2. The second load simulation device 5-2 applies a load to the second output shaft 19-2, and the second torque and speed sensor 4-2 detects the actual output torque and actual speed of the second output shaft 19-2. At this time, the second electromagnetic proportional reversing valve 12-2 is in a closed state, and the second hydraulic motor 7-2 does not output power to the outside; S2, electro-hydraulic hybrid transmission single pump single side working mode experiment: c. The industrial computer controls the first motor 1-1 and the first hydraulic motor 7-1 to start at the same time. The first motor 1-1 drives the first input shaft 18-1 to rotate, and the first gear group decelerates and outputs the first input shaft 19-1. The first load simulation device 5-1 applies a load to the first output shaft 19-1, and detects the actual output torque and actual speed of the first output shaft 19-1 through the first torque speed sensor 4-1. The first load simulation device 5-1 is load-adjusted to set the upper limit value of the current of the first motor 1-1. As the load of the first load simulation device 5-1 increases, the current of the first motor 1-1 will increase accordingly. When the current value of the first motor 1-1 read by the first current sensor exceeds the upper limit value, the first electromagnetic proportional reversing valve 12-1 is opened, and the first hydraulic pump station 10-1 supplies oil to the first hydraulic motor 7-1. The first hydraulic motor 7-1 starts to work. After the first hydraulic motor 7-1 is locked with the first one-way clutch 8-1, auxiliary power is input to the first torque coupler 3-1 through the second input shaft 18-2. d, or the industrial computer controls the second motor 1-2 and the second hydraulic motor 7-2 to start at the same time, the second motor 1-2 drives the third input shaft 18-3 to rotate, and after being decelerated by the second gear set, it is output through the first output shaft 19-1, the second load simulation device 5-2 applies a load to the second output shaft 19-2, and detects the actual output torque and actual speed of the second output shaft 19-2 through the second torque speed sensor 4-2, and sets the upper limit value of the current of the second motor 1-2 by load adjustment of the second load simulation device 5-2. As the load of the second load simulation device 5-2 increases, the current of the second motor 1-2 will increase accordingly. When the current value of the second motor 1-2 read by the second current sensor exceeds the upper limit value, the second electromagnetic proportional reversing valve 12-2 opens, the second hydraulic pump station 10-2 supplies oil to the second hydraulic motor 7-2, and the second hydraulic motor 7-2 starts to work. After the second hydraulic motor 7-2 is locked with the second one-way clutch 8-2, auxiliary power is input to the second torque coupler 3-2 through the fourth input shaft 18-4; S3, Electro-hydraulic hybrid transmission dual-pump dual-side joint working mode experiment: e. The industrial computer controls the first motor 1-1 and the first hydraulic pump station 10-1 to start. The first motor 1-1 drives the first input shaft 18-1 to rotate, and the first output shaft 19-1 outputs the first output shaft 19-1 after deceleration by the first gear set. The first load simulation device 5-1 applies a load to the first output shaft 19-1, and detects the actual output torque and actual speed of the first output shaft 19-1 through the first torque and speed sensor 4-1. At this time, the first electromagnetic proportional reversing valve 12-1 is in a closed state, and the first hydraulic motor 7-1 does not output power to the outside. The first load simulation device 5-1 Carry out load adjustment and set the upper limit value of the current of the first motor 1-1. As the load of the first load simulation device 5-1 increases, the current of the first motor 1-1 will increase accordingly. When the current value of the first motor 1-1 read by the first current sensor exceeds the upper limit value, the first electromagnetic proportional reversing valve 12-1 opens, and the first hydraulic pump station 10-1 supplies oil to the first hydraulic motor 7-1. The first hydraulic motor 7-1 starts to work. After the first hydraulic motor 7-1 is locked with the first one-way clutch 8-1, auxiliary power is input to the first torque coupler 3-1 through the second input shaft 18-2. f, at the same time, the industrial computer controls the second motor 1-2 and the second hydraulic pump station 10-2 to start, the second motor 1-2 drives the third input shaft 18-3 to rotate, and after being decelerated by the third gear set, it is output through the second output shaft 19-2, the second load simulation device 5-2 applies a load to the second output shaft 19-2, and detects the actual output torque and actual speed of the second output shaft 19-2 through the second torque and speed sensor 4-2. At this time, the second electromagnetic proportional reversing valve 12-2 is in a closed state, the second hydraulic motor 7-2 does not output power to the outside, and the second load simulation device 5- 2 performs load adjustment, sets the upper limit value of the current of the second motor 1-2, and as the load of the second load simulation device 5-2 increases, the current of the second motor 1-2 will increase accordingly. When the current value of the second motor 1-2 read by the second current sensor exceeds the upper limit value, the second electromagnetic proportional reversing valve 12-2 opens, the second hydraulic pump station 10-2 supplies oil to the second hydraulic motor 7-2, and the second hydraulic motor 7-2 starts to work. After the second hydraulic motor 7-2 is locked with the second one-way clutch 8-2, auxiliary power is input to the second torque coupler 3-2 through the fourth input shaft 18-4; g. When the opening of the first electromagnetic proportional reversing valve 12-1 reaches the maximum, the power of the first hydraulic motor 7-1 reaches the upper limit, and the output torque of the first output shaft 19-1 still cannot match the load of the first load simulation device 5-1, the second hydraulic motor 7-2 continues to open the second electromagnetic proportional reversing valve 12-2 under the condition of meeting the power demand of the second output shaft 19-2. At the same time, the industrial computer controls the second electromagnetic proportional valve 11-2 to open, so that the second hydraulic pump station 10-2 inputs the surplus hydraulic oil into the first hydraulic circuit through the second one-way compensation oil pipe 16-2, so that the auxiliary power of the first hydraulic motor 7-1 is further improved, so that the first output shaft 19-1 can match the load of the first load simulation device 5-1; h, or when the opening of the second electromagnetic proportional reversing valve 12-2 reaches the maximum, the power of the second hydraulic motor 7-2 reaches the upper limit, and the output torque of the second output shaft 19-2 still cannot match the load of the second load simulation device 5-2, the first hydraulic motor 7-1 continues to open the first electromagnetic proportional reversing valve 12-1 while meeting the power requirement of the first output shaft 19-1. At the same time, the industrial computer controls the first electromagnetic proportional valve 11-1 to open, so that the first hydraulic pump station 10-1 inputs the surplus hydraulic oil into the second hydraulic circuit through the first one-way compensation oil pipe 16-1, so that the auxiliary power of the second hydraulic motor 7-2 is further improved, so that the second output shaft 19-2 can match the load of the second load simulation device 5-2.

[0046] The embodiments described above are only used to illustrate the technical solutions of the present invention, rather than to limit them. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that the technical solutions described in the aforementioned embodiments may still be modified, or some of the technical features may be replaced by equivalents. Such modifications or replacements will not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the various embodiments of the present invention.

Claims

1. An electro-hydraulic hybrid transmission system test bench, comprising a first electro-hydraulic hybrid simulation unit and a second electro-hydraulic hybrid simulation unit simulating two cutting parts of a coal mining machine, characterized in that: The first electro-hydraulic hybrid simulation unit comprises a first motor (1-1) for inputting torque, a first hydraulic motor (7-1) and a first load simulation device (5-1) for applying a load to the output torque, wherein the first load simulation device (5-1) applies a load to the output torque to change the current in the first motor (1-1), and a first current sensor for detecting a current value is installed on the first motor (1-1); The second electro-hydraulic hybrid simulation unit comprises a second motor (1-2) for inputting torque, a second hydraulic motor (7-2) and a second load simulation device (5-2) for applying a load to the output torque, wherein the second load simulation device (5-2) applies a load to the output torque to change the current in the second motor (1-2), and a second current sensor for detecting a current value is installed on the second motor (1-2); A first hydraulic circuit in the first electric-hydraulic hybrid simulation unit comprises a first hydraulic pump station (10-1) connected to an oil inlet of a first hydraulic motor (7-1) and an oil cylinder (17) connected to an oil discharge port of the first hydraulic motor (7-1), wherein the oil cylinder (17) is connected to the first hydraulic pump station (10-1); A second hydraulic circuit in the second electric-hydraulic hybrid simulation unit comprises a second hydraulic pump station (10-2) connected to an oil inlet of a second hydraulic motor (7-2) and an oil cylinder (17) connected to an oil discharge port of the second hydraulic motor (7-2), wherein the oil cylinder (17) is connected to the second hydraulic pump station (10-2); A first oil delivery pipe (15-1) is connected between the first hydraulic pump station (10-1) and the first hydraulic motor (7-1), a second oil delivery pipe (15-2) is connected between the second hydraulic pump station (10-2) and the second hydraulic motor (7-2), and a first one-way compensation oil pipe (16-1) capable of delivering hydraulic oil in the first oil delivery pipe (15-1) to the second oil delivery pipe (15-2) and a second one-way compensation oil pipe (16-2) capable of delivering hydraulic oil in the second oil delivery pipe (15-2) to the first oil delivery pipe (15-1) are respectively connected between the first oil delivery pipe (15-1) and the second oil delivery pipe (15-2); A first electromagnetic proportional valve (11-1) is provided in the first one-way compensation oil pipe (16-1), and a second electromagnetic proportional valve (11-2) is provided in the second one-way compensation oil pipe (16-2); When the current value detected by the first current sensor increases, the opening of the second electromagnetic proportional valve (11-2) increases proportionally, or when the current value detected by the second current sensor increases, the opening of the first electromagnetic proportional valve (11-1) increases proportionally.

2. The electro-hydraulic hybrid transmission system test bench according to claim 1, characterized in that: The first electric-hydraulic hybrid simulation unit also includes a first torque coupler (3-1), the first motor (1-1) and the first hydraulic motor (7-1) are respectively connected to the first torque coupler (3-1) so that the power inputted by each motor is coupled in parallel, and the torque is outputted through the first output shaft (19-1) of the first torque coupler (3-1), and the first output shaft (19-1) is connected to the first load simulation device (5-1); The first torque coupler (3-1) comprises two input shafts, namely a first input shaft (18-1) and a second input shaft (18-2); the first input shaft (18-1) is connected to the first output shaft (19-1) via a first gear set, and the first input shaft (18-1) is connected to the first motor (1-1); the second input shaft (18-2) is connected to the first input shaft (18-1) via a second gear set, and the second input shaft (18-2) is connected to the first hydraulic motor (7-1); and a first one-way clutch (8-1) is provided between the second input shaft (18-2) and the first hydraulic motor (7-1); The second electric-hydraulic hybrid simulation unit also includes a second torque coupler (3-2), the second motor (1-2) and the second hydraulic motor (7-2) are respectively connected to the second torque coupler (3-2) so that the power inputted by each motor is coupled in parallel, and the torque is outputted through the second output shaft (19-2) of the second torque coupler (3-2), and the second output shaft (19-2) is connected to the second load simulation device (5-2); The second torque coupler (3-2) includes two input shafts, namely a third input shaft (18-3) and a fourth input shaft (18-4); the third input shaft (18-3) is transmission-connected to the second output shaft (19-2) via a third gear set, and the third input shaft (18-3) is connected to the second motor (1-2); the fourth input shaft (18-4) is transmission-connected to the third input shaft (18-3) via a fourth gear set, the fourth input shaft (18-4) is connected to the second hydraulic motor (7-2), and a second one-way clutch (8-2) is provided between the fourth input shaft (18-4) and the second hydraulic motor (7-2).

3. The electro-hydraulic hybrid transmission system test bench according to claim 2, characterized in that: The first motor (1-1) and the second motor (1-2) are both three-phase asynchronous motors.

4. The electro-hydraulic hybrid transmission system test bench according to claim 1, characterized in that: The first load simulation device (5-1) and the second load simulation device (5-2) are both magnetic powder brakes.

5. The electro-hydraulic hybrid transmission system test bench according to claim 4, characterized in that: A first torque speed sensor (4-1) is connected between the first load simulation device (5-1) and the first output shaft (19-1); and a second torque speed sensor (4-2) is connected between the second load simulation device (5-2) and the second output shaft (19-2).

6. The electro-hydraulic hybrid transmission system test bench according to claim 1, characterized in that: A first electromagnetic proportional reversing valve (12-1) is provided in the first hydraulic circuit, the P port of the first electromagnetic proportional reversing valve (12-1) is connected to the oil outlet of the first hydraulic pump station (10-1), the A port of the first electromagnetic proportional reversing valve (12-1) is connected to the first oil delivery pipe (15-1), the oil discharge port of the first hydraulic motor (7-1) is connected to the B port of the first electromagnetic proportional reversing valve (12-1), and the T port of the first electromagnetic proportional reversing valve (12-1) is connected to the oil cylinder (17); A second electromagnetic proportional reversing valve (12-2) is provided in the second hydraulic circuit, the P port of the second electromagnetic proportional reversing valve (12-2) is connected to the oil outlet of the second hydraulic pump station (10-2), the A port of the second electromagnetic proportional reversing valve (12-2) is connected to the second oil delivery pipe (15-2), the oil discharge port of the second hydraulic motor (7-2) is connected to the B port of the second electromagnetic proportional reversing valve (12-2), and the T port of the second electromagnetic proportional reversing valve (12-2) is connected to the oil cylinder (17); A first high-pressure relief valve (9) is connected in parallel at both ends of the first hydraulic pump station (10-1); A second high-pressure relief valve (13) is connected in parallel at both ends of the second hydraulic pump station (10-2); The T port of the first electromagnetic proportional reversing valve (12-1) and the T port of the second electromagnetic proportional reversing valve (12-2) are both connected to the low-pressure relief valve (14), and the low-pressure relief valve (14) is connected to the oil cylinder (17).

7. The electro-hydraulic hybrid transmission system test bench according to claim 6, characterized in that: The first electromagnetic proportional reversing valve (12-1) and the second electromagnetic proportional reversing valve (12-2) both have a Y-type neutral position function.

8. The electro-hydraulic hybrid transmission system test bench according to claim 7, characterized in that: When the current value of the first motor (1-1) exceeds a set upper limit value, the first electromagnetic proportional reversing valve (12-1) opens, and its opening increases proportionally with the increase of the current value; when the current value of the second motor (1-2) exceeds a set upper limit value, the second electromagnetic proportional reversing valve (12-2) opens, and its opening increases proportionally with the increase of the current value.

9. The electro-hydraulic hybrid transmission system test bench according to claim 8, characterized in that: It also includes an industrial computer, which is electrically connected to the first hydraulic pump station (10-1), the first motor (1-1), the first load simulation device (5-1), the first electromagnetic proportional reversing valve (12-1), the first electromagnetic proportional valve (11-1), the first torque speed sensor (4-1), the first current sensor, the second hydraulic pump station (10-2), the second motor (1-2), the second load simulation device (5-2), the second electromagnetic proportional reversing valve (12-2), the second electromagnetic proportional valve (11-2), the second torque speed sensor (4-2) and the second current sensor.

10. The simulation experiment method of the electric-hydraulic hybrid transmission system test bench according to any one of claims 1 to 9, characterized in that: The specific steps are as follows: S1, pure motor working mode experiment: a. The industrial computer controls the first motor (1-1) and the first hydraulic pump station (10-1) to start, the first motor (1-1) drives the first input shaft (18-1) to rotate, and the first gear group decelerates and outputs the first input shaft (19-1). The first load simulation device (5-1) applies a load to the first output shaft (19-1), and the first torque and speed sensor detects the actual output torque and actual speed of the first output shaft (19-1). At this time, the first electromagnetic proportional reversing valve (12-1) is in a closed state, and the first hydraulic motor (7-1) does not output power to the outside; b. At the same time, the industrial computer controls the second motor (1-2) and the second hydraulic pump station (10-2) to start, the second motor (1-2) drives the third input shaft (18-3) to rotate, and after being decelerated by the third gear set, the output is output through the second output shaft (19-2), the second load simulation device (5-2) applies a load to the second output shaft (19-2), and the actual output torque and actual speed of the second output shaft (19-2) are detected by the second torque and speed sensor. At this time, the second electromagnetic proportional reversing valve (12-2) is in a closed state, and the second hydraulic motor (7-2) does not output power to the outside; S2, electro-hydraulic hybrid transmission single pump single side working mode experiment: c. The industrial computer controls the first motor (1-1) and the first hydraulic motor (7-1) to start simultaneously, the first motor (1-1) drives the first input shaft (18-1) to rotate, and the first gear group decelerates and outputs the first input shaft (19-1). The first load simulation device (5-1) applies a load to the first output shaft (19-1), and detects the actual output torque and actual speed of the first output shaft (19-1) through the first torque and speed sensor. The first load simulation device (5-1) is load-regulated to set the upper limit of the current of the first motor (1-1). value, as the load of the first load simulation device (5-1) increases, the current of the first motor (1-1) will increase accordingly, when the current value of the first motor (1-1) read by the first current sensor exceeds the upper limit value, the first electromagnetic proportional reversing valve (12-1) opens, the first hydraulic pump station (10-1) supplies oil to the first hydraulic motor (7-1), the first hydraulic motor (7-1) starts to work, and after the first hydraulic motor (7-1) and the first one-way clutch (8-1) are locked, auxiliary power is input to the first torque coupler (3-1) through the second input shaft (18-2); d, or the industrial computer controls the second motor (1-2) and the second hydraulic motor (7-2) to start simultaneously, the second motor (1-2) drives the third input shaft (18-3) to rotate, and after being decelerated by the second gear set, the third input shaft (18-3) is output through the first output shaft (19-1), the second load simulation device (5-2) applies a load to the second output shaft (19-2), and the actual output torque and actual speed of the second output shaft (19-2) are detected by the second torque and speed sensor, and the current upper limit of the second motor (1-2) is set by load adjustment of the second load simulation device (5-2). value, as the load of the second load simulation device (5-2) increases, the current of the second motor (1-2) will increase accordingly, when the current value of the second motor (1-2) read by the second current sensor exceeds the upper limit value, the second electromagnetic proportional reversing valve (12-2) opens, the second hydraulic pump station (10-2) supplies oil to the second hydraulic motor (7-2), the second hydraulic motor (7-2) starts to work, and after the second hydraulic motor (7-2) and the second one-way clutch (8-2) are locked, auxiliary power is input to the second torque coupler (3-2) through the fourth input shaft (18-4); S3, Electro-hydraulic hybrid transmission dual-pump dual-side joint working mode experiment: e. The industrial computer controls the first motor (1-1) and the first hydraulic pump station (10-1) to start, the first motor (1-1) drives the first input shaft (18-1) to rotate, and after being decelerated by the first gear set, the first input shaft (18-1) is output through the first output shaft (19-1), the first load simulation device (5-1) applies a load to the first output shaft (19-1), and detects the actual output torque and actual speed of the first output shaft (19-1) through the first torque speed sensor. At this time, the first electromagnetic proportional reversing valve (12-1) is in a closed state, the first hydraulic motor (7-1) does not output power to the outside, and the first load simulation device (5-1) is loaded. Load regulation, setting the upper limit value of the current of the first motor (1-1), as the load of the first load simulation device (5-1) increases, the current of the first motor (1-1) will increase accordingly, when the first current sensor reads that the current value of the first motor (1-1) exceeds the upper limit value, the first electromagnetic proportional reversing valve (12-1) opens, the first hydraulic pump station (10-1) supplies oil to the first hydraulic motor (7-1), the first hydraulic motor (7-1) starts to work, and after the first hydraulic motor (7-1) and the first one-way clutch (8-1) are locked, auxiliary power is input to the first torque coupler (3-1) through the second input shaft (18-2); f, at the same time, the industrial computer controls the second motor (1-2) and the second hydraulic pump station (10-2) to start, the second motor (1-2) drives the third input shaft (18-3) to rotate, and after being decelerated by the third gear set, the output is output through the second output shaft (19-2), the second load simulation device (5-2) applies a load to the second output shaft (19-2), and detects the actual output torque and actual speed of the second output shaft (19-2) through the second torque and speed sensor, at this time, the second electromagnetic proportional reversing valve (12-2) is in a closed state, the second hydraulic motor (7-2) does not output power to the outside, and the second load simulation device (5-2) is in a closed state. Carry out load regulation, set the upper limit value of the current of the second motor (1-2), as the load of the second load simulation device (5-2) increases, the current of the second motor (1-2) will increase accordingly, when the second current sensor reads that the current value of the second motor (1-2) exceeds the upper limit value, the second electromagnetic proportional reversing valve (12-2) opens, the second hydraulic pump station (10-2) supplies oil to the second hydraulic motor (7-2), the second hydraulic motor (7-2) starts to work, and after the second hydraulic motor (7-2) and the second one-way clutch (8-2) are locked, auxiliary power is input to the second torque coupler (3-2) through the fourth input shaft (18-4); g. When the opening of the first electromagnetic proportional reversing valve (12-1) reaches the maximum, the power of the first hydraulic motor (7-1) reaches the upper limit, and the output torque of the first output shaft (19-1) still cannot match the load of the first load simulation device (5-1), the second electromagnetic proportional reversing valve (12-2) continues to open under the condition that the power requirement of the second output shaft (19-2) is met. At the same time, the industrial computer controls the second electromagnetic proportional valve (11-2) to open, so that the second hydraulic pump station (10-2) inputs the surplus hydraulic oil into the first hydraulic circuit through the second one-way compensation oil pipe (16-2), so that the auxiliary power of the first hydraulic motor (7-1) is further improved, so that the first output shaft (19-1) can match the load of the first load simulation device (5-1); h, or when the opening of the second electromagnetic proportional reversing valve (12-2) reaches the maximum, the power of the second hydraulic motor (7-2) reaches the upper limit, and the output torque of the second output shaft (19-2) still cannot match the load of the second load simulation device (5-2), the first hydraulic motor (7-1) continues to open the first electromagnetic proportional reversing valve (12-1) under the condition that the power requirement of the first output shaft (19-1) is met. At the same time, the industrial computer controls the first electromagnetic proportional valve (11-1) to open, so that the first hydraulic pump station (10-1) inputs the surplus hydraulic oil into the second hydraulic circuit through the first one-way compensation oil pipe (16-1), so that the auxiliary power of the second hydraulic motor (7-2) is further improved, so that the second output shaft (19-2) can match the load of the second load simulation device (5-2).

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