An electro-hydraulic hybrid transmission system test bench and simulation experiment method thereof

Abstract

The present invention discloses an electro-hydraulic hybrid transmission system test bench and a simulation experiment method thereof, which respectively include two electro-hydraulic hybrid simulation units simulating the two cutting parts of a coal mining machine. The two electro-hydraulic hybrid simulation units are respectively provided with an electric motor and a hydraulic motor for input torque, and a load simulation device connected to the output torque. The load output by the load simulation device is a change in the current of the motor, thereby controlling the operation of the hydraulic motor. Two one-way hydraulic one-way compensation oil pipes are provided between the two hydraulic circuits of the two hydraulic motors, so that the hydraulic oil can be complemented between the two hydraulic circuits. Through the above-mentioned structural scheme, the present invention can simulate three modes of the cutting part of the coal mining machine: 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. The feasibility of the structural scheme and the control method are verified through the mode experiment to solve the practical difficulties in the design experiment of the cutting part of the coal mining machine.

Description

Technical Field

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

[0002] With my country's economic development and increasing demand for energy, coal mining volumes are increasing, mining times are long, and mining equipment often suffers from power shortages. Therefore, the trend toward larger and more powerful coal mining equipment has become a major development trend in the coal mining machinery market. Due to the uneven thickness of coal seams across the country and the complex geological conditions, cutting in complex coal seams can encounter sudden changes in coal seam hardness or coal rock distribution. This results in large load fluctuations, high loads, and uneven cutting loads for coal mining machines. Furthermore, the left and right cutting drums of coal mining machines operate in different vertical positions, resulting in uneven cutting loads on the left and right sides.

[0003] However, due to space constraints within the shearer and the coal seam, the shearer cannot be equipped with a high-power flameproof inverter, and the shearer's cutting section cannot adjust torque. To address this issue, traditional shearer solutions design the drum and transformer based on the user-provided geological conditions of the working face. This essentially determines the cutting speed and maximum power, and the design is based on maximum power requirements. Working faces with different geological conditions require re-adapting the cutting drum, and the shearer model is selected based on the maximum power requirements.

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

[0005] Traditional shearer cutting units are powered by a three-phase asynchronous motor, while the shearer's cutting arm is powered by a hydraulic pump station. When the shearer is working on the face, the hydraulic pump station is first activated to raise or lower the arm to the target height, then locked. The hydraulic pump station then idles in standby mode, and the cutting motor then activates to begin cutting and mining. While the hydraulic pump station is being adjusted, no cutting occurs; while cutting is being carried out, the hydraulic pump station idles in standby mode. Therefore, the hydraulic pump station wastes energy that could be used in the cutting unit. Furthermore, preliminary research indicates that adjusting the traction speed and cutting torque based on changing 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 destruction of the rocker arm housing, resulting in large 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, 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 actual difficulties in the design experiment of the cutting part of the coal mining machine. Summary of the Invention

[0008] To address the above issues, 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:

[0009] 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.

[0010] 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. The first load simulation device applies a load to the output torque to change the current in the first motor. The first motor is equipped with a first current sensor for detecting the current value.

[0011] 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;

[0012] The first hydraulic circuit in the first electro-hydraulic hybrid simulation unit includes a first hydraulic pump station connected to the oil inlet of the first hydraulic motor and a cylinder connected to the oil unloading port of the first hydraulic motor, wherein the cylinder is connected to the first hydraulic pump station;

[0013] The second hydraulic circuit in the second electro-hydraulic hybrid simulation unit includes a second hydraulic pump station connected to the oil inlet of the second hydraulic motor and a cylinder connected to the oil unloading port of the second hydraulic motor, wherein the cylinder is connected to the second hydraulic pump station;

[0014] 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;

[0015] 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;

[0016] 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.

[0017] Furthermore, the first electro-hydraulic hybrid simulation unit further includes a first torque coupler, the first electric motor and the first hydraulic motor are respectively connected to the first torque coupler so that their respective input power is coupled in parallel, and torque is output through a first output shaft of the first torque coupler, and the first output shaft is connected to the first load simulation device;

[0018] 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;

[0019] The second electro-hydraulic hybrid simulation unit further includes a second torque coupler, the second electric motor and the second hydraulic motor are respectively connected to the second torque coupler so that their respective input power is coupled in parallel, and torque is output through a second output shaft of the second torque coupler, and the second output shaft is connected to the second load simulation device;

[0020] The second torque coupler includes two input shafts, namely a third input shaft and a fourth input shaft. The third input shaft is connected to the second output shaft through a third gear set, and the third input shaft is connected to the second motor; the fourth input shaft is connected to the third input shaft through a fourth gear set, and the fourth input shaft is connected to the second hydraulic motor, and a second one-way clutch is provided between the fourth input shaft and the second hydraulic motor.

[0021] Furthermore, the first motor and the second motor are both three-phase asynchronous motors.

[0022] Furthermore, the first load simulation device and the second load simulation device are both magnetic powder brakes.

[0023] 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.

[0024] Furthermore, a first electromagnetic proportional reversing valve is provided in the first hydraulic circuit, the P port of the first electromagnetic proportional reversing valve is connected to the oil outlet of the first hydraulic pump station, the A port of the first electromagnetic proportional reversing valve is connected to the first oil delivery pipe, the oil unloading port of the first hydraulic motor is connected to the B port of the first electromagnetic proportional reversing valve, and the T port of the first electromagnetic proportional reversing valve is connected to the oil cylinder;

[0025] 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 unloading 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;

[0026] A first high-pressure relief valve is connected in parallel at both ends of the first hydraulic pump station;

[0027] A second high-pressure relief valve is connected in parallel at both ends of the second hydraulic pump station;

[0028] 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.

[0029] Furthermore, the first electromagnetic proportional reversing valve and the second electromagnetic proportional reversing valve both have a Y-type neutral position function.

[0030] Furthermore, 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.

[0031] Furthermore, it also includes an industrial control 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.

[0032] Furthermore, a simulation experiment method of an electro-hydraulic hybrid transmission system test bench has the following specific steps:

[0033] S1, pure motor working mode experiment:

[0034] 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. After being decelerated by the first gear set, the output is output through the first output shaft. The first load simulation device applies a load to the first output shaft, and the first torque and speed sensor detects the actual output torque and actual speed of the first output shaft. At this time, the first electromagnetic proportional reversing valve is in the closed state, and the first hydraulic motor does not output power to the outside.

[0035] b. Simultaneously, 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, which is then decelerated by the third gear set and outputted through the second output 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 speed of the second output shaft. At this time, the second electromagnetic proportional reversing valve is closed, and the second hydraulic motor does not output power.

[0036] S2, electro-hydraulic hybrid transmission single pump single-side working mode experiment:

[0037] c. The industrial computer controls the first motor and the first hydraulic motor to start simultaneously. The first motor drives the first input shaft to rotate, and after being decelerated by the first gear set, the output is output through the first output shaft. 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 load simulation device is load-regulated to set the upper limit 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, 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, auxiliary power is input to the first torque coupler through the second input shaft;

[0038] d. Or the industrial computer controls the second motor and the second hydraulic motor to start simultaneously, the second motor drives the third input shaft to rotate, and the output 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. By load-adjusting the second load simulation device, the upper limit value of the second motor current is set. 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, auxiliary power is input to the second torque coupler through the fourth input shaft;

[0039] S3, electro-hydraulic hybrid transmission dual-pump dual-side joint working mode experiment:

[0040] e. The industrial computer controls the start-up of the first motor and the first hydraulic pump station. The first motor drives the first input shaft to rotate, which is output through the first output 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, auxiliary power is input to the first torque coupler through the second input shaft;

[0041] 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 current value of the second motor read by the second current sensor 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. The second hydraulic motor starts to work. After the second hydraulic motor is locked with the second one-way clutch, auxiliary power is input to the second torque coupler through the fourth input shaft;

[0042] g. When the opening of the first electromagnetic proportional reversing valve reaches its maximum, the power of the first hydraulic motor reaches its 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 second hydraulic motor meets the power requirement of the second output shaft. At the same time, the industrial computer controls the opening of the second electromagnetic proportional valve, causing the second hydraulic pump station to input excess hydraulic oil into the first hydraulic circuit through the second one-way compensation oil pipe, thereby further increasing the auxiliary power of the first hydraulic motor and enabling the first output shaft to match the load of the first load simulation device;

[0043] 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 that the power requirement of the first output shaft is met. 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 improved, so that the second output shaft can match the load of the second load simulation device.

[0044] Compared with the prior art, the advantages of the present invention are as follows:

[0045] 1. The present invention, through the design of a test bench with the above structure, can simulate and test three modes of the shearer's cutting section: pure motor operation mode test, electro-hydraulic hybrid transmission single-pump single-side operation mode test, and electro-hydraulic hybrid transmission dual-pump dual-side combined operation mode test. Through these mode experiments, the feasibility of the structural scheme and control method is verified, thus overcoming the practical difficulties in the design and testing of the shearer's cutting section.

[0046] 2. The invention takes into account the existing dual-height pump station on the existing coal mining machine and uses it as the auxiliary power source of this experimental platform. It designs a torque-coupled electro-hydraulic hybrid transmission system for the cutting part of the coal mining machine, fully utilizing the existing hydraulic power of the coal mining machine and saving layout space. It further couples the power of the coal mining machine height pump station with the power of 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 to timely supplement the kinetic energy of the coal mining machine drum, avoid the problems of overload and stall of the coal mining machine cutting motor, and reduce the risk of cutting motor failure.

[0047] 3. The present invention utilizes a torque coupling mechanism to achieve torque coupling between power sources, which can fully utilize the torque-increasing effect of the auxiliary power source and achieve the goal of optimal distribution of the comprehensive torque of the coal cutting section. The torque coupling device can avoid the problem of difficult installation due to limited space, reduce the difficulty of processing and installation, and achieve the goal of maximizing cutting efficiency and optimizing the overall coal mining performance.

[0048] 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 oil cylinder, thereby providing a guarantee for the power demand of the hydraulic motor.

[0049] 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, thereby conducting a study on 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 a timely manner to provide support for the conclusion summary after the test. BRIEF DESCRIPTION OF THE DRAWINGS

[0050] Figure 1 This is a layout diagram of the electro-hydraulic hybrid transmission system test bench of the present invention;

[0051] Figure 2 This is a hydraulic-mechanical schematic diagram of the electro-hydraulic hybrid transmission system test bench of the present invention;

[0052] Figure 3 This is a power principle diagram of the pure motor working mode of the present invention;

[0053] Figure 4 This is a power principle diagram of the electro-hydraulic hybrid transmission single pump single-side working mode of the present invention;

[0054] Figure 5 This is the power principle diagram of the electro-hydraulic hybrid transmission dual-pump dual-side joint working mode mode 1 of the present invention;

[0055] Figure 6 This is the power principle diagram mode 2 of the electro-hydraulic hybrid transmission dual-pump dual-side joint working mode of the present invention;

[0056] Figure 7 This is a structural diagram of the electro-hydraulic hybrid system of the present invention;

[0057] Figure 8 This is a structural diagram of the assembly platform located at the bottom of the electro-hydraulic hybrid;

[0058] Figure 9 It is the structural diagram of the connection end of the one-way clutch;

[0059] Reference numerals:

[0060] 1-1, first motor; 1-2, second motor;

[0061] 2-1, first coupling; 2-2, second coupling;

[0062] 3-1, first torque coupler; 3-2, second torque coupler;

[0063] 4-1, first torque and speed sensor; 4-2, second torque and speed sensor;

[0064] 5-1. First load simulation device; 5-2. Second load simulation device;

[0065] 6. Assembly platform;

[0066] 7-1, first hydraulic motor; 7-2, second hydraulic motor;

[0067] 8-1, first one-way clutch; 8-2, second one-way clutch; 8-3, inner race; 8-4, outer race; 8-5, roller; 8-6, spring;

[0068] 9. First high-pressure relief valve; 13. Second high-pressure relief valve; 14. Low-pressure relief valve;

[0069] 10-1, first hydraulic pump station; 10-2, second hydraulic pump station;

[0070] 11-1, first solenoid proportional valve; 11-2, second solenoid proportional valve;

[0071] 12-1, first electromagnetic proportional reversing valve; 12-2, second electromagnetic proportional reversing valve;

[0072] 15-1, first oil pipeline; 15-2, second oil pipeline;

[0073] 16-1, first one-way compensation oil pipe; 16-2, second one-way compensation oil pipe;

[0074] 17. Oil cylinder;

[0075] 18-1, first input shaft; 18-2, second input shaft; 18-3, third input shaft; 18-4, fourth input shaft;

[0076] 19-1, first output shaft; 19-2, second output shaft;

[0077] 20. First slide groove; 21. Second slide groove; 22. Third slide groove; 23. Mounting hole; 24. Assembly platform. DETAILED DESCRIPTION

[0078] 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.

[0079] 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.

[0080] In the description of the invention, it should be noted that terms such as "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer" indicate positions or locations based on those shown in the accompanying drawings. These terms are intended solely to facilitate and simplify the description of the invention and are not intended to indicate or imply that the devices or components referred to have a specific orientation, be constructed, or operate in a specific manner. Therefore, they should not be construed as limitations on the invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0081] In the description of the invention, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood broadly. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; direct or indirect connections through an intermediary; and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in the invention based on the specific circumstances. Example 1

[0082] like Figure 1 As 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.

[0083] 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 a load to the output torque. The first load simulation device 5-1 applies a 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, causing the current in the first motor 1-1 to change. A first current sensor for detecting the current value is installed on the first motor 1-1.

[0084] 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 .

[0085] The first motor 1 - 1 is a three-phase asynchronous motor, and a first current sensor is connected to the first motor 1 - 1 .

[0086] 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 their respective input powers are coupled in parallel, and torque is output through a first output shaft of the first torque coupler 3-1. The first output shaft is connected to the first load simulation device 5-1.

[0087] The first torque coupler 3-1 includes two input shafts: 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 via a first coupling 2-1. The second output shaft 19-2 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. A first one-way clutch 8-1 is provided between the second input shaft 18-2 and the first hydraulic motor 7-1.

[0088] 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 a load to the output torque. The second load simulation device 5-2 applies a 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, causing the current in the second motor 1-2 to change. The second motor 1-2 is equipped with a second current sensor for detecting the current value.

[0089] 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 .

[0090] The second motor 1 - 2 is a three-phase asynchronous motor, and a second current sensor is connected to the second motor 1 - 2 .

[0091] 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 their respective input power is coupled in parallel, and torque is output through a second output shaft of the second torque coupler 3-2. The second output shaft is connected to the second load simulation device 5-2.

[0092] The second torque coupler 3-2 includes two input shafts: a third input shaft 18-3 and a fourth input shaft 18-4. The third input shaft 18-3 is connected to the second output shaft 19-2 via a third gear set, and is also connected to the second motor 1-2 via a second coupling 2-2. The fourth input shaft 18-4 is connected to the third input shaft 18-3 via a fourth gear set and 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

[0093] like Figure 1As shown, it also includes a first hydraulic circuit and a second hydraulic circuit.

[0094] 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 has a Y-type neutral 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. 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, the first electromagnetic proportional reversing valve 12 - 1 opens, and its opening increases proportionally with the increase of the current value.

[0095] 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, the second hydraulic circuit is provided with a second electromagnetic proportional reversing valve 12-2, which has a Y-type neutral 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, the second electromagnetic proportional reversing valve 12 - 2 opens, and its opening increases proportionally with the increase of the current value.

[0096] Connected between the first oil pipeline 15-1 and the second oil pipeline 15-2 are a first one-way compensating oil pipeline 16-1, capable of transferring hydraulic oil from the first oil pipeline 15-1 to the second oil pipeline 15-2, and a second one-way compensating oil pipeline 16-2, capable of transferring hydraulic oil from the second oil pipeline 15-2 to the first oil pipeline 15-1. A first solenoid proportional valve 11-1 is installed in the first one-way compensating oil pipeline 16-1, and a second solenoid proportional valve 11-2 is installed in the second one-way compensating oil pipeline 16-2. When the current flowing through the first motor 1-1 increases, the opening of the second solenoid proportional valve 11-2 increases proportionally. Similarly, when the current flowing through the second motor 1-2 increases, the opening of the first solenoid proportional valve 11-1 increases proportionally. Example 3

[0097] 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 to create a pressure difference between the inlet and outlet of the hydraulic motor. The specific scheme is as follows:

[0098] like Figure 1 As shown,

[0099] The first high-pressure relief valve 9 is connected in parallel at both ends of the first hydraulic pump station 10-1;

[0100] A second high-pressure relief valve 13 is connected in parallel at both ends of the second hydraulic pump station 10-2;

[0101] 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

[0102] In order to facilitate the control of electro-hydraulic hybrid operation and record experimental data, the present invention has further improvements, the specific solutions are as follows:

[0103] It also includes an industrial control 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

[0104] In order to make the test bench modular, the present invention has the following improvements, the specific solutions are as follows:

[0105] like Figure 7 and Figure 8 As shown, the assembly platform 624 for the test bench has a first chute 20 located in the middle of the assembly platform 624. The first chute 20 is plugged into the torque coupler of the electro-hydraulic hybrid. A second chute 21 and a third chute 22 are located perpendicular to the first chute 20. The second chute 21 corresponds to the input shaft of the torque coupler. A hydraulic motor is slidably connected to the second chute 21. By sliding in the second chute 21, the hydraulic motor can adjust the distance between the hydraulic motor and the input shaft, facilitating the installation or removal of the one-way clutch. The third chute 22 corresponds to the output shaft of the torque coupler. A magnetic powder brake is slidably connected to the third chute 22. By sliding the magnetic powder brake in the third chute 22, the distance between the magnetic powder brake and the output shaft can be adjusted, facilitating the installation or removal of the torque rotation sensor. A mounting hole 23 is located on the other side of the first chute 20. This mounting hole 23 corresponds to the input shaft on the other side of the torque coupler. The motor is mounted in this mounting hole 23. Example 6

[0106] 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 consists of an inner ring 8-3, an outer ring 8-4, a roller 8-5, and a spring 8-6. Outer ring 8-4 is fixedly connected to the input end of the torque coupler shaft, while inner ring 8-3 is fixedly connected to the output shaft of the hydraulic motor. Multiple evenly spaced right-angled cuts are arranged along the circumference of inner ring 8-3. Springs 8-6 are installed on the vertical sections of these cuts, parallel to the horizontal sections. Rollers 8-5 are installed on the outer ends of these springs 8-6.

[0107] When the inner ring 8-3 and the outer ring 8-4 rotate in opposite directions, Figure 9 As 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.

[0108] 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 and the outer ring 8-4. Therefore, the hydraulic motor cannot drive the input shaft of the torque coupler to rotate:

[0109] When the direction of the hydraulic motor is consistent with that of its input shaft and its speed is greater than the input shaft speed, the balls are subjected to sufficient centrifugal force to move outward, causing the roller 8-5 to contact the outer ring 8-4 and lock into a whole. At this time, the hydraulic motor drives the input shaft of the torque coupler to rotate.

[0110] 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

[0111] like Figures 2 to 5 As shown in the figure, the simulation experimental method of the electro-hydraulic hybrid transmission system test bench has the following specific steps:

[0112] S1, pure motor working mode experiment:

[0113] 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. After deceleration by the first gear set, the output is transmitted 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 the first torque and speed sensor 4-1 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 closed, and the first hydraulic motor 7-1 does not output power.

[0114] 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. 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 4-2. At this time, the second electromagnetic proportional reversing valve 12-2 is in the closed state, and the second hydraulic motor 7-2 does not output power to the outside.

[0115] S2, electro-hydraulic hybrid transmission single pump single-side working mode experiment:

[0116] c. The industrial computer controls the simultaneous start-up of the first motor 1-1 and the first hydraulic motor 7-1. The first motor 1-1 drives the first input shaft 18-1 to rotate. After being decelerated by the first gear set, the first output shaft 19-1 outputs the power. 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. The first load simulation device 5-1 is load-regulated to set the upper limit 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 increases accordingly. When the current value of the first motor 1-1 read by the first current sensor exceeds the upper limit, 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 operate. 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.

[0117] 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 output 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 and speed sensor 4-2. By load adjustment of the second load simulation device 5-2, the upper limit value of the current of the second motor 1-2 is set. 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, and 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. 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.

[0118] S3, electro-hydraulic hybrid transmission dual-pump dual-side joint working mode experiment:

[0119] 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. After being decelerated by the first gear set, the output 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 and speed sensor 4-1. At this time, the first electromagnetic proportional reversing valve 12-1 is in the closed state, the first hydraulic motor 7-1 does not output power to the outside, and the first load simulation device 5-1 Perform load regulation and set the upper limit 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, 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, and 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.

[0120] 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 4-2. At this time, the second electromagnetic proportional reversing valve 12-2 is in the 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 regulation and sets the upper limit 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 increases accordingly. When the current value of the second motor 1-2 read by the second current sensor exceeds the upper limit, 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 operate. 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.

[0121] 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 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 reversing 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 increased, so that the first output shaft 19-1 can match the load of the first load simulation device 5-1;

[0122] 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.

[0123] The embodiments described above are only used to illustrate the technical solutions of the present invention, rather than to limit the same. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some of the technical features therein. However, these 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 the 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 the current value is installed on the second motor (1-2); A first hydraulic circuit in the first electro-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 electro-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 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 their respective input powers are coupled in parallel, and torque is output through a first output shaft (19-1) of the first torque coupler (3-1); the first output shaft (19-1) 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). The second input shaft (18-2) is connected to the first input shaft (18-1) through a second gear set. 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 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 their respective input powers are coupled in parallel, and torque is output through a second output shaft (19-2) of the second torque coupler (3-2); 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 connected to the second output shaft (19-2) through 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 connected to the third input shaft (18-3) through a fourth gear set, and 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 and 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 and 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 unloading 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: The invention also includes an industrial control 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.

10. The simulation experiment method of the electro-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 after being decelerated by the first gear set, the output 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 the actual output torque and actual speed of the first output shaft (19-1) are detected by the first torque and speed sensor. 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 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, 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. 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 and speed sensor. By load-regulating the first load simulation device (5-1), the upper limit of the current of the first motor (1-1) is set. 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 output 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 output 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 and 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 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); 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. Carrying out load regulation, setting 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 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); 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 by the second hydraulic motor (7-2). 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 increased, 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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