Test control system of hydraulic motor

Abstract

The invention provides a test control system of a hydraulic motor. The test control system comprises a high-pressure pump set, a low-pressure pump set, a pressure regulating valve set, a control valve set and a winch system. The high-pressure pump set is connected with a first oil port of a tested motor, and the low-pressure pump set is connected with a second oil port of the motor; the pressure regulating valve group is respectively connected with the high-pressure pump group and the low-pressure pump group, the control valve group is respectively connected with the low-pressure pump group, the high-pressure pump group, a first oil port of the motor and a second oil port of the motor, and the winch system is connected with the motor. According to the invention, the motor can be tested in the pump working condition, so that the comprehensiveness of test data of the motor is improved.

Description

Technical Field

[0001] The present invention belongs to the technical field of hydraulic control, and in particular relates to a test control system for a hydraulic motor. Background Art

[0002] Before use, hydraulic motors need to be tested to verify whether they meet design specifications, such as pressure, speed, efficiency, etc.

[0003] In the related art, when testing a hydraulic motor, the motor is usually driven to rotate through a test control system to detect whether the motor meets the requirements of the actual scene. The test control system includes a pump group, a reversing valve, and a balancing valve. The pump group is used to provide high-pressure oil to the motor, and the pump group and the motor are connected through a reversing valve and a balancing valve. The return oil port of the pump group is connected to the oil inlet of the reversing valve, the first working oil port of the reversing valve is connected to the oil inlet of the balancing valve, the return oil port of the balancing valve is connected to the oil inlet of the motor, and the return oil port of the motor is connected to the control oil port of the balancing valve and the second working oil port of the reversing valve. The return oil port of the reversing valve is connected to the oil tank. When the motor needs to rotate forward, the pump group is controlled to start, and the high-pressure oil output by the pump group enters the motor after passing through the reversing valve and the balancing valve. If the motor needs to reverse, the reversing valve can be controlled to reverse.

[0004] However, in the above test, only the forward and reverse rotation of the motor are detected, and the motor is not directly connected to the load, so the motor is always in the motor working condition, that is, the motor rotation direction is the same as the output torque direction, which makes the test result incomplete. Summary of the invention

[0005] The embodiment of the present disclosure provides a test control system for a hydraulic motor, which can improve the comprehensiveness of the data during the motor test. The technical solution is as follows:

[0006] The embodiment of the present disclosure provides a test control system for a hydraulic motor, the test control system comprising a high-pressure pump group, a low-pressure pump group, a pressure regulating valve group, a control valve group and a winch system; the control valve group is respectively connected to the low-pressure pump group, the high-pressure pump group, the first oil port of the motor and the second oil port of the motor, and the control valve group is configured to: deliver the oil pumped by the high-pressure pump group to the first oil port of the motor, and recover the oil output from the second oil port of the motor in an oil tank to drive the motor to rotate forward; or deliver the oil pumped by the low-pressure pump group to the first oil port of the motor, and recover the oil output from the second oil port of the motor in an oil tank to drive the motor to rotate forward; The second oil port of the motor, and the oil output from the first oil port of the motor is recovered in the oil tank to drive the motor to reverse; the pressure regulating valve group is connected to the high-pressure pump group and the low-pressure pump group respectively, and the pressure regulating valve group is used to adjust the oil pressure of the oil pumped by the high-pressure pump group at the first oil port of the motor and adjust the oil pressure of the oil pumped by the low-pressure pump group at the second oil port of the motor, so that when the motor rotates forward or reverse, the oil pressure at the first oil port of the motor is greater than the oil pressure at the second oil port of the motor; the winch system is connected to the motor.

[0007] In another implementation of the present disclosure, the high-pressure pump group includes a first motor, a first variable pump unit and a metering pump; the first motor is connected to the first variable pump unit and the metering pump respectively, and the return oil port of the first variable pump unit is connected to the control valve group; the first variable pump unit includes a first pump body, a first variable cylinder, a first shuttle valve, a first displacement control valve and a first pressure control valve; the rod chamber of the first variable cylinder is connected to the variable mechanism of the first pump body, the rodless chamber of the first variable cylinder is connected to the working oil port of the first displacement control valve, and the first displacement control valve The oil inlet of the first pressure control valve is connected to the working oil port of the first pressure control valve, and the oil return port of the first displacement control valve is connected to the oil tank; the first oil port of the first shuttle valve is connected to the oil return port of the metering pump, and the second oil port of the first shuttle valve is connected to the oil return port of the first pump body; the oil inlet of the first pressure control valve is connected to the oil return port of the first shuttle valve, and the oil return port of the first pressure control valve is connected to the oil tank, the first control oil port of the first pressure control valve is connected to the pressure regulating valve group, and the second control oil port of the first pressure control valve is connected to the oil return port of the first shuttle valve.

[0008] In another implementation of the present disclosure, the pressure regulating valve group includes a first proportional pressure reducing valve and a first solenoid reversing valve, the oil inlet of the first proportional pressure reducing valve is connected to the oil return port of the metering pump, the oil return port of the first proportional pressure reducing valve is connected to the oil inlet of the first solenoid reversing valve, the control oil port of the first proportional pressure reducing valve is connected to its own oil return port, and the oil drain port of the first proportional pressure reducing valve is connected to the oil tank; the working oil port of the first solenoid reversing valve is connected to the first control oil port of the first pressure control valve, and the oil return port of the first solenoid reversing valve is connected to the oil tank.

[0009] In another implementation of the present disclosure, the low-pressure pump group includes a second motor and a second variable pump unit, the second motor is connected to the second variable pump unit, and the oil return port of the second variable pump unit is connected to the control valve group; the pressure regulating valve group also includes a second proportional pressure reducing valve and a second solenoid reversing valve, the oil inlet of the second proportional pressure reducing valve is connected to the oil return port of the metering pump, the oil return port of the second proportional pressure reducing valve is connected to the oil inlet of the second solenoid reversing valve, and the control oil port of the second proportional pressure reducing valve is connected to its own oil return port; the working oil port of the second solenoid reversing valve is connected to the second variable pump unit, and the oil return port of the second solenoid reversing valve is connected to the oil tank.

[0010] In another implementation of the present disclosure, the pressure regulating valve group also includes a control oil overflow valve, the oil inlet of the control oil overflow valve is respectively connected to the oil return port of the metering pump and the first oil port of the first shuttle valve, the oil return port of the control oil overflow valve is connected to the oil tank, and the control oil port of the control oil overflow valve is connected to its own oil inlet.

[0011] In another implementation of the present disclosure, the control valve group includes a high-pressure check valve, a high-pressure relief valve unit, a low-pressure check valve and a low-pressure relief valve unit; the oil inlet of the high-pressure check valve is connected to the oil return port of the high-pressure pump group, the oil return port of the high-pressure check valve is connected to its own hydraulic control port, and the oil return port of the high-pressure check valve is connected to the first oil port of the motor; the oil inlet of the high-pressure relief valve unit is respectively connected to the oil return port of the high-pressure check valve and the first oil port of the motor, the oil return port of the high-pressure relief valve unit is respectively connected to the oil inlet of the low-pressure relief valve unit, the second oil port of the motor and the oil return port of the low-pressure check valve, and the high-pressure relief valve unit is configured The oil pressure at the oil inlet of the high-pressure relief valve unit is higher than a first threshold value, the oil flowing in from the oil inlet of the high-pressure relief valve unit is discharged from the oil return port of the high-pressure relief valve unit; the oil inlet of the low-pressure check valve is connected to the oil return port of the low-pressure pump group, and the hydraulic control port of the low-pressure check valve is connected to its own oil return port; the oil return port of the low-pressure relief valve unit is connected to the oil tank, and the low-pressure relief valve unit is configured as follows: when the oil pressure at the oil inlet of the low-pressure relief valve unit is higher than a second threshold value, the oil flowing in from the oil inlet of the low-pressure relief valve unit is discharged from the oil return port of the low-pressure relief valve unit, and the first threshold value is greater than the second threshold value.

[0012] In another implementation of the present disclosure, the high-pressure relief valve unit includes a first control check valve and a first control relief valve, the oil inlet of the first control check valve is respectively connected to the first oil port of the motor and the oil return port of the high-pressure check valve, and the oil return port of the first control check valve is respectively connected to the oil return port of the first control relief valve, the oil inlet of the low-pressure relief valve unit, the oil return port of the low-pressure check valve, and the second oil port of the motor;

[0013] The control oil port of the first control check valve is connected to the oil inlet of the first control relief valve, and the control oil port of the first control relief valve is connected to its own oil inlet.

[0014] In another implementation of the present disclosure, the control valve group also includes a total control overflow valve, the oil inlet of the total control overflow valve is respectively connected to the first oil port of the motor and the oil return port of the first control check valve, the oil return port of the total control overflow valve is connected to the oil tank, and the control oil port of the total control overflow valve is connected to its own oil inlet.

[0015] In another implementation of the present disclosure, the test control system also includes a locking valve group, which also includes a locking shuttle valve, a locking solenoid reversing valve and a locking cartridge valve, the first oil port of the locking shuttle valve is respectively connected to the oil return port of the high-pressure check valve and the oil inlet port of the locking cartridge valve, the second oil port of the locking shuttle valve is connected to the first oil port of the motor, the oil return port of the locking shuttle valve is connected to the oil inlet port of the locking solenoid reversing valve, the oil return port of the locking solenoid reversing valve is connected to the oil tank, the working oil port of the locking solenoid reversing valve is connected to the control oil port of the locking cartridge valve, and the oil return port of the locking cartridge valve is connected to the first oil port of the motor.

[0016] In another implementation of the present disclosure, the test control system further includes a safety valve group, which includes a safety cartridge valve, a first safety relief valve, a second safety relief valve and a safety solenoid reversing valve; the oil inlet of the safety cartridge valve is respectively connected to the oil return port of the locking cartridge valve, the first oil port of the motor and the oil inlet of the first safety relief valve, and the oil return port of the safety cartridge valve is respectively connected to the second oil port of the motor and the oil inlet of the low-pressure relief valve unit; the oil return port of the first safety relief valve The oil inlet of the second safety relief valve is connected to the oil tank, and the control oil port of the first safety relief valve is connected to its own oil inlet; the oil inlet of the second safety relief valve is connected to the working oil port of the safety electromagnetic reversing valve, the oil return port of the second safety relief valve is connected to the oil tank, and the control oil port of the second safety relief valve is connected to its own oil inlet; the oil inlet of the safety electromagnetic reversing valve is connected to the control oil port of the safety cartridge valve and the oil inlet of the first safety relief valve, and the oil return port of the safety electromagnetic reversing valve is connected to the oil tank.

[0017] The technical solution provided by the embodiments of the present disclosure has the following beneficial effects:

[0018] When the test control system provided by the embodiment of the present disclosure is used to control the motor, since the test control system includes a winch system and the winch system is connected to the motor, the motor can be operated according to actual working conditions by driving the winch to release or reel in the rope, thereby ensuring the comprehensiveness of the data during the motor test.

[0019] Moreover, since the test control system also includes a high-pressure pump group, a low-pressure pump group, a pressure regulating valve group, and a control valve group, and the control valve group is configured to: deliver the oil pumped by the high-pressure pump group to the first oil port of the motor, and recover the oil output from the second oil port of the motor in the oil tank to drive the motor to rotate forward; or, deliver the oil pumped by the low-pressure pump group to the second oil port of the motor, and recover the oil output from the first oil port of the motor in the oil tank to drive the motor to rotate reversely, in this way, the high-pressure pump group can be used to supply oil to the first oil port of the motor to drive the motor to rotate forward, or the low-pressure pump group can be used to supply oil to the second oil port of the motor to drive the motor to rotate reversely.

[0020] Since the pressure regulating valve group is used to make the oil pressure at the first oil port of the motor greater than the oil pressure at the second oil port of the motor when the motor rotates forward or reverse, the oil inlet of the motor is a high-pressure oil port when the motor rotates forward, and the motor is in motor working condition, and the winch retracts the rope. When the motor rotates reversely, the oil inlet of the motor is a low-pressure oil port when the motor rotates reversely, and the oil inlet of the motor is a low-pressure oil port when the motor rotates reversely.

[0021] Therefore, the above test control system can put the motor in different working conditions, and then conduct comprehensive tests on the motor, ultimately improving the comprehensiveness of the test data. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] In order to more clearly illustrate the technical solutions in the embodiments of the present disclosure, the drawings required for use in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present disclosure. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0023] Figure 1 It is a schematic diagram of the principle of a test control system provided by an embodiment of the present disclosure;

[0024] Figure 2 yes Figure 1 Enlarged view of the lower middle part;

[0025] Figure 3 yes Figure 2 Enlarged view of the lower left part;

[0026] Figure 4 yes Figure 2 Enlarged view of the upper middle part;

[0027] Figure 5 yes Figure 2 Enlarged view of the lower right part;

[0028] Figure 6 yes Figure 1 Enlarged view of the upper right part;

[0029] Figure 7 yes Figure 1 Enlarged view of the upper left part.

[0030] The symbols in the figure mean the following:

[0031] 1. High-pressure pump group; 11. First motor; 12. First variable pump unit; 120. First pump body; 121. First variable cylinder; 122. First shuttle valve; 123. First displacement control valve; 124. First pressure control valve; 13. Dosing pump;

[0032] 2. low-pressure pump group; 21. second motor; 22. second variable pump unit; 220. second pump body; 221. second variable cylinder; 222. second shuttle valve; 223. second displacement control valve; 224. second pressure control valve;

[0033] 3. Pressure regulating valve group; 31. First proportional pressure reducing valve; 32. First solenoid reversing valve; 33. Second proportional pressure reducing valve; 34. Second solenoid reversing valve; 35. Control oil overflow valve;

[0034] 4. Control valve group; 41. High-pressure one-way valve; 42. High-pressure relief valve unit; 421. First control one-way valve; 422. First control relief valve; 43. Low-pressure one-way valve; 44. Low-pressure relief valve unit; 45. Speed ​​regulating valve; 46. Main control relief valve; 47. Pressure reducing valve; 48. First control reversing valve; 49. Second control reversing valve;

[0035] 5. Locking valve group; 51. Locking shuttle valve; 52. Locking solenoid reversing valve; 53. Locking cartridge valve;

[0036] 6. Safety valve group; 61. Safety cartridge valve; 62. Safety first relief valve; 63. Safety second relief valve; 64. Safety solenoid reversing valve;

[0037] 100, motor; 101, forced large displacement valve; 102, high frequency response valve; 103, motor variable cylinder;

[0038] 200. Winch system. DETAILED DESCRIPTION

[0039] In order to make the objectives, technical solutions and advantages of the present disclosure more clear, the embodiments of the present disclosure will be further described in detail below with reference to the accompanying drawings.

[0040] In the related art, when testing the motor 100, since only the forward and reverse rotation of the motor 100 is detected, the motor 100 is not directly connected to the load, so the motor 100 is always in the motor working condition, that is, the rotation direction of the motor 100 is the same as the output torque direction, which makes the test result incomplete. When the motor 100 is actually working, the motor 100 can be in the pump working condition or the motor working condition. For example, when the motor 100 drives the winch to collect or release the rope. When the winch collects the rope, the motor 100 needs to rotate forward. The motor 100 works in the motor working condition. The rotation direction of the output shaft of the motor 100 is the same as the direction of the output torque. At this time, the first oil port of the motor 100 is for oil intake and the second oil port is for oil return. The first oil port of the motor 100 is a high-pressure oil port. When the winch releases the rope, due to the gravity of the rope, the rope will drag the motor 100 to rotate in the opposite direction. At this time, the motor 100 needs to drag the rope to avoid overspeed when the rope falls. Therefore, the motor 100 works in a pump condition. The rotation direction of the output shaft of the motor 100 is opposite to the output torque direction. The second oil port of the motor 100 is for oil intake and the first oil port is for oil return. The first oil port of the motor 100 is a high-pressure oil port. However, since the second oil port of the motor 100 is for oil intake and the first oil port is for oil return, the test system in the related art is obviously impossible to achieve the above purpose. Therefore, additional valves are required to control the oil pressure of the first oil port to be greater than the oil pressure of the second oil port. Therefore, in order to solve the above problems, the present disclosure proposes a test control system for the hydraulic motor 100 that is different from the related art.

[0041] Figure 1 is a schematic diagram of a test control system provided by an embodiment of the present disclosure, such as Figure 1 As shown, the test control system includes a high-pressure pump group 1, a low-pressure pump group 2, a pressure regulating valve group 3, a control valve group 4 and a winch system 200. The control valve group 4 is connected to the low-pressure pump group 2, the high-pressure pump group 1, the first oil port of the motor 100 and the second oil port of the motor 100 respectively.

[0042] The control valve group 4 is configured to: when the motor 100 rotates forward, the high-pressure pump group 1 can pump oil into the first oil port of the motor 100, and the oil in the second oil port of the motor 100 is recovered in the oil tank, or when the motor 100 rotates reversely, the low-pressure pump group 2 can pump oil into the second oil port of the motor 100, and the oil in the first oil port of the motor 100 is recovered in the oil tank. The pressure regulating valve group 3 is connected to the high-pressure pump group 1 and the low-pressure pump group 2 respectively, and the pressure regulating valve group 3 is used to adjust the oil pressure of the oil pumped by the high-pressure pump group 1 at the first oil port of the motor 100 and the oil pressure of the oil pumped by the low-pressure pump group 2 at the second oil port of the motor 100, so that when the motor 100 rotates forward or reversely, the oil pressure at the first oil port of the motor 100 is greater than the oil pressure at the second oil port of the motor 100. The winch system 200 is connected to the motor 100.

[0043] When the test control system provided by the embodiment of the present disclosure is used to control the motor 100, since the test control system includes a winch system 200, and the winch system 200 is connected to the motor 100, the motor 100 can be made to work according to actual working conditions by driving the winch to release or reel in the rope, thereby ensuring the comprehensiveness of the data during the motor test.

[0044] Moreover, since the test control system also includes a high-pressure pump group 1, a low-pressure pump group 2, a pressure regulating valve group 3, and a control valve group 4, and the control valve group 4 is configured to: deliver the oil pumped by the high-pressure pump group 1 to the first oil port of the motor 100, and recover the oil output from the second oil port of the motor 100 in the oil tank to drive the motor 100 to rotate forward; or, deliver the oil pumped by the low-pressure pump group 2 to the second oil port of the motor 100, and recover the oil output from the first oil port of the motor 100 in the oil tank to drive the motor 100 to rotate reversely, in this way, the high-pressure pump group 1 can be used to provide oil to the first oil port of the motor to drive the motor 100 to rotate forward, or the low-pressure pump group 2 can be used to provide oil to the second oil port of the motor 100 to drive the motor 100 to rotate reversely.

[0045] Since the pressure regulating valve group 3 is used to make the oil pressure at the first oil port of the motor 100 greater than the oil pressure at the second oil port of the motor 100 when the motor 100 rotates forward or reverse, the oil inlet of the motor 100 is a high-pressure oil port when the motor 100 rotates forward, and the motor 100 is in a motor working state, and the winch retracts the rope. When the motor 100 rotates reversely, the oil inlet of the second oil port is oiled, and the oil return of the first oil port is oiled, and the oil inlet of the motor 100 is a low-pressure oil port, and the motor 100 is in a pump working state, and the winch releases the rope.

[0046] Therefore, the above test control system can put the motor 100 in different working conditions, thereby performing a comprehensive test on the motor 100, and ultimately improving the comprehensiveness of the test data.

[0047] Figure 2 yes Figure 1 The enlarged view of the lower middle part is as follows: Figure 2 As shown, optionally, the high pressure pump group 1 comprises a first motor 11, a first variable pump unit 12 and a metering pump 13. The first motor 11 is connected to the first variable pump unit 12 and the metering pump 13 respectively, and the oil return port of the first variable pump unit 12 is connected to the control valve group 4.

[0048] Figure 3 yes Figure 2 The enlarged image of the lower left part, combined with Figure 3The first variable pump unit 12 includes a first pump body 120, a first variable cylinder 121, a first shuttle valve 122, a first displacement control valve 123, and a first pressure control valve 124. The rod chamber of the first variable cylinder 121 is connected to the variable mechanism of the first pump body 120, the rodless chamber of the first variable cylinder 121 is connected to the working oil port of the first displacement control valve 123, the oil inlet of the first displacement control valve 123 is connected to the working oil port of the first pressure control valve 124, and the oil return port of the first displacement control valve 123 is connected to the oil tank. The first oil port of the first shuttle valve 122 is connected to the oil return port of the metering pump 13, and the second oil port of the first shuttle valve 122 is connected to the oil return port of the first pump body 120. The oil inlet of the first pressure control valve 124 is connected to the oil return port of the first shuttle valve 122, the oil return port of the first pressure control valve 124 is connected to the oil tank, the first control oil port of the first pressure control valve 124 is connected to the working oil port of the first solenoid reversing valve 32, and the second control oil port of the first pressure control valve 124 is connected to the oil return port of the first shuttle valve 122.

[0049] In the above implementation, the first motor 11 is used to drive the first variable pump unit 12 and the metering pump 13 to work. The first variable pump unit 12 is used to pump high-pressure oil to the first oil port A of the motor 100. The metering pump 13 is used to provide control oil for the pressure regulating valve group 3.

[0050] The first displacement control valve 123 is used to adjust the maximum displacement of the first pump body 120 , and the first pressure control valve 124 is used to adjust the maximum working pressure of the first pump body 120 .

[0051] In normal state, the right spring force of the first displacement control valve 123 is greater than the left spring force, the first displacement control valve 123 works in the right position, the working oil port A of the first displacement control valve 123 is connected with the oil return port T, A→T. The oil in the rodless chamber of the first variable cylinder 121 is drained through the working oil port A→oil return port T of the first displacement control valve 123. The piston of the first variable cylinder 121 is at the far left under the action of the left spring tension of the first displacement control valve 123, and the first pump body 120 is at the maximum displacement.

[0052] When the first motor 11 is started, the pressure oil in the oil return port of the first pump body 120 directly enters the rod chamber of the first variable cylinder 121; the other way of the pressure oil in the oil return port of the first pump body 120 passes through the first pressure control valve 124 and the first displacement control valve 123 in sequence and enters the rodless chamber of the first variable cylinder 121. Therefore, when there is no control signal from the first pressure control valve 124 and the first displacement control valve 123, the first pressure control valve 124 and the first displacement control valve 123 both work in the right position, the oil inlet P of the first pressure control valve 124 is connected to the working oil port A, and the working oil port A of the first displacement control valve 123 is connected to the oil return port T, and the oil in the rodless chamber of the first variable cylinder 121 is discharged into the oil tank. The piston rod of the first variable cylinder 121 is retracted into the cylinder body. The first pump body 120 is on standby at the minimum displacement state. When the first displacement control valve 123 has a signal, the first displacement control valve 123 works in the left position, and the larger the control signal of the first displacement control valve 123 is, the larger the connecting opening between the oil inlet P and the working oil port A of the first displacement control valve 123 is, and correspondingly, the larger the flow rate of the oil entering the rodless chamber of the first variable cylinder 121 is, the larger the maximum displacement of the first pump body 120 is, that is, the first displacement control valve 123 determines the maximum displacement of the first pump body 120.

[0053] When the pressure of the return oil port of the first pump body 120 is less than the set value of the first pressure control valve 124, the first pressure control valve 124 works in the right position, the opening between the oil inlet P→working oil port A of the first pressure control valve 124 is the largest (P→A of the first pressure control valve 124 is fully open), and the first pump body 120 works at the maximum displacement. When the pressure of the return oil port of the first pump body 120 reaches the set value of the first pressure control valve 124, the first pressure control valve 124 works in the left position, the opening between the oil inlet P→working oil port A of the first pressure control valve 124 becomes smaller, and the A→T opening becomes larger, the first pump body 120 changes, the output flow rate is adapted to the system demand flow rate, and the oil pressure of the return oil port of the first pump body 120 remains unchanged.

[0054] The second control oil port X2 and the first control oil port X1 of the first pressure control valve 124 are respectively connected to the oil return port C of the first shuttle valve 122 and the pressure regulating valve group 3. The pressure at the first oil port A of the first shuttle valve 122 is connected to the oil return port of the metering pump 13, and the second oil port of the first shuttle valve 122 is connected to the oil return port of the first pump body 120. Therefore, the pressure at the oil return port C of the first shuttle valve 122 is always the higher pressure at the first oil port A and the second oil port B.

[0055] In this embodiment, the oil pressure action area of ​​the first control oil port X1 of the first pressure control valve 124 is much larger than the oil pressure action area of ​​the second control oil port X2. That is, the setting value of the first pressure control valve 124 basically depends only on the pressure at the first control oil port X1 of the first pressure control valve 124, that is, depends on the pressure of the pressure regulating valve group 3.

[0056] Figure 4 yes Figure 2 The enlarged picture of the upper middle part, combined with Figure 4 Optionally, the pressure regulating valve group 3 includes a first proportional pressure reducing valve 31 and a first electromagnetic reversing valve 32. The oil inlet of the first proportional pressure reducing valve 31 is connected to the oil return port of the metering pump 13, the oil return port of the first proportional pressure reducing valve 31 is connected to the oil inlet of the first electromagnetic reversing valve 32, and the control oil port of the first proportional pressure reducing valve 31 is connected to its own oil return port. The oil drain port of the first proportional pressure reducing valve 31 is connected to the oil tank. The working oil port of the first electromagnetic reversing valve 32 is connected to the first control oil port of the first pressure control valve 124, which is used to control the output pressure and displacement of the first pump body 120, and the oil return port of the first electromagnetic reversing valve 32 is connected to the oil tank.

[0057] The first proportional pressure reducing valve 31 is used to adjust the output pressure and displacement of the first pump body 120. Since the minimum adjustment pressure of the first proportional pressure reducing valve 31 is non-zero, in order to reduce the minimum setting pressure of the first pump body 120 to improve the safety during the test and save energy and reduce consumption, a first electromagnetic reversing valve 32 is provided at the oil return port of the first proportional pressure reducing valve 31. When the first electromagnetic reversing valve 32 is energized, the first electromagnetic reversing valve 32 works in the right position, the oil inlet P of the first electromagnetic reversing valve 32 is connected with the working oil port A, P→A, and the first proportional pressure reducing valve 31 can adjust the pressure. When the first electromagnetic reversing valve 32 loses power, the first electromagnetic reversing valve 32 works in the left position, the oil at the first control oil port X1 of the first pressure control valve 124 is drained through the working oil port A→oil return port T of the first electromagnetic reversing valve 32, and the setting pressure of the first variable pump unit 12 is the lowest.

[0058] Combination Figure 2 Optionally, the low-pressure pump group 2 includes a second motor 21 and a second variable pump unit 22 , the second motor 21 is connected to the second variable pump unit 22 , and the oil return port of the second variable pump unit 22 is connected to the control valve group 4 .

[0059] Combination Figure 4 The pressure regulating valve group 3 also includes a second proportional pressure reducing valve 33 and a second electromagnetic reversing valve 34. The oil inlet of the second proportional pressure reducing valve 33 is connected to the oil return port of the metering pump 13, the oil return port of the second proportional pressure reducing valve 33 is connected to the oil inlet of the second electromagnetic reversing valve 34, and the control oil port of the second proportional pressure reducing valve 33 is connected to its own oil return port. The working oil port of the second electromagnetic reversing valve 34 is connected to the second variable pump unit 22, which is used to control the output pressure and displacement of the second variable pump unit 22, and the oil return port of the second electromagnetic reversing valve 34 is connected to the oil tank.

[0060] In the above implementation, the second motor 21 is used to drive the second variable pump unit 22 to work. The second variable pump unit 22 is used to pump pressure oil to the second oil port B of the motor 100. The second proportional pressure reducing valve 33 is used to adjust the output pressure and displacement of the second variable pump unit 22.

[0061] The working principle of the above low-pressure pump group 2 is similar to that of the high-pressure pump group 1, and will not be repeated here.

[0062] Optionally, the pressure regulating valve group 3 also includes a control oil overflow valve 35, the oil inlet of the control oil overflow valve 35 is respectively connected to the oil return port of the metering pump 13 and the first oil port of the first shuttle valve 122 and the second oil port of the second shuttle valve 222, the oil return port of the control oil overflow valve 35 is connected to the oil tank, and the control oil port of the control oil overflow valve 35 is connected to its own oil inlet.

[0063] When the oil return port pressure of the first pump body 120 is lower than the set pressure (for example, 3.5 MPa) of the control oil relief valve 35 (such as when the high-pressure pump is in low-pressure standby), the first oil port of the first shuttle valve 122 is connected to the oil return port, and the oil path in the first shuttle valve 122 is A→C. The oil at the oil return port of the first pump body 120 enters the rod chamber of the first variable cylinder 121, so that the first pump body 120 quickly returns to the minimum displacement standby state, thereby saving energy and reducing consumption.

[0064] Figure 5 yes Figure 2 The enlarged image of the lower right part, combined with Figure 5 Optionally, the second variable pump unit 22 includes a second pump body 220, a second variable cylinder 221, a second shuttle valve 222, a second displacement control valve 223, and a second pressure control valve 224. The rod chamber of the second variable cylinder 221 is connected to the variable mechanism of the second pump body 220, the rodless chamber of the second variable cylinder 221 is connected to the working oil port of the second displacement control valve 223, the oil inlet of the second displacement control valve 223 is connected to the working oil port of the second pressure control valve 224, and the oil return port of the second displacement control valve 223 is connected to the oil tank. The second oil port of the second shuttle valve 222 is connected to the oil return port of the metering pump 13, and the second oil port of the second shuttle valve 222 is connected to the oil return port of the second pump body 220. The oil inlet of the second pressure control valve 224 is connected to the oil return port of the second shuttle valve 222, the oil return port of the second pressure control valve 224 is connected to the oil tank, the first control oil port of the second pressure control valve 224 is connected to the working oil port of the second solenoid reversing valve 34, and the second control oil port of the second pressure control valve 224 is connected to the oil return port of the second shuttle valve 222.

[0065] The second variable pump unit 22 has the same structure as the first variable pump unit 12. The working principle of the second variable pump unit 22 can be found in the first variable pump unit 12 above, and will not be described again here.

[0066] Figure 6 yes Figure 1 The enlarged image of the upper right part of the middle Figure 6 Optionally, the control valve group 4 includes a high-pressure check valve 41, a high-pressure relief valve unit 42, a low-pressure check valve 43 and a low-pressure relief valve unit 44. The oil inlet of the high-pressure check valve 41 is connected to the oil return port of the high-pressure pump group 1, the oil return port of the high-pressure check valve 41 is connected to its own hydraulic control port, and the oil return port of the high-pressure check valve 41 is connected to the first oil port of the motor 100.

[0067] The oil inlet of the high-pressure overflow valve unit 42 is respectively connected to the oil return port of the high-pressure check valve 41 and the first oil port of the motor 100, and the oil return port of the high-pressure overflow valve unit 42 is respectively connected to the oil inlet of the low-pressure overflow valve unit 44, the second oil port of the motor 100 and the oil return port of the low-pressure check valve 43. The high-pressure overflow valve unit 42 is configured as follows: when the oil pressure of the oil at the oil inlet of the high-pressure overflow valve unit 42 is higher than the first threshold value, the oil flowing into the oil inlet of the high-pressure overflow valve unit 42 is discharged from the oil return port of the high-pressure overflow valve unit 42.

[0068] The oil inlet of the low-pressure one-way valve 43 is connected to the oil return port of the low-pressure pump group 2, and the hydraulic control port of the low-pressure one-way valve 43 is connected to its own oil return port.

[0069] The oil return port of the low-pressure overflow valve unit 44 is connected to the oil tank, and the low-pressure overflow valve unit 44 is configured as follows: when the oil pressure of the oil at the oil inlet of the low-pressure overflow valve unit 44 exceeds the second threshold value, the oil flowing into the oil inlet of the low-pressure overflow valve unit 44 will be discharged from the oil return port of the low-pressure overflow valve unit 44, and the first threshold value is greater than the second threshold value.

[0070] In the above implementation, the high-pressure check valve 41 is used to prevent the high-pressure oil from flowing back into the first pump body 120 when the first oil port A of the motor 100 returns oil, thereby damaging the first pump body 120 or causing the first pump body 120 to reverse. The high-pressure relief valve unit 42 is used as a safety valve, and its set pressure is always higher than the maximum pressure corresponding to the first pressure control valve 124. The low-pressure check valve 43 is used to prevent the low-pressure oil from flowing back into the second pump body 220 when the second oil port B of the motor 100 returns oil, thereby damaging or causing the second pump body 220 to reverse. The low-pressure relief valve unit 44 is used as a safety valve, and its set pressure is always higher than the maximum pressure corresponding to the second pressure control valve 224.

[0071] Optionally, the high-pressure relief valve unit 42 includes a first control check valve 421 and a first control relief valve 422, the oil inlet of the first control check valve 421 is connected to the first oil port A of the motor 100 and the oil return port of the high-pressure check valve 41, respectively, and the oil return port of the first control check valve 421 is connected to the oil return port of the first control relief valve 422, the oil inlet of the low-pressure relief valve unit 44, the oil return port of the low-pressure check valve 43, and the second oil port of the motor 100. The control oil port of the first control check valve 421 is connected to the oil inlet of the first control relief valve 422, the oil return port of the first control relief valve 422 is connected to the oil return port of the first control check valve 421, and the control oil port of the first control relief valve 422 is connected to its own oil inlet.

[0072] In the above-mentioned implementation of releasing the rope, the first control one-way valve 421 is used to limit the flow direction of the oil, and the first control overflow valve 422 is used to limit the pressure when the first oil port A of the motor 100 returns the oil.

[0073] The low-pressure relief valve unit 44 has the same structure as the high-pressure relief valve unit 42 and will not be described in detail herein.

[0074] Optionally, the control valve group 4 also includes a speed regulating valve 45 and a total control overflow valve 46, the oil inlet of the speed regulating valve 45 is respectively connected to the first oil port of the motor 100 and the oil inlet of the first control check valve 421, the oil return port of the speed regulating valve 45 is connected to the oil inlet of the total control overflow valve 46, the oil return port of the total control overflow valve 46 is connected to the oil tank, and the control oil port of the total control overflow valve 46 is connected to its own oil inlet.

[0075] In the above implementation, the speed regulating valve 45 is used to limit the maximum flow into the total control relief valve 46 to prevent the pressure regulation from failing due to exceeding the working range of the total control relief valve 46. The total control relief valve 46 is used to adjust the relief pressure of the brake control oil circuit.

[0076] Optionally, the control valve group 4 also includes a pressure reducing valve 47, a first control reversing valve 48 and a second control reversing valve 49, the oil inlet of the pressure reducing valve 47 is respectively connected to the oil return port of the speed regulating valve 45 and the oil inlet of the main control overflow valve 46, the oil return port of the pressure reducing valve 47 is connected to the oil inlet of the first control reversing valve 48, and the control oil port of the pressure reducing valve 47 is connected to its own oil return port.

[0077] The oil return port of the first control reversing valve 48 is connected to the oil tank, the working oil port of the first control reversing valve 48 is connected to the oil inlet port of the second control reversing valve 49, the oil return port of the second control reversing valve 49 is connected to the oil tank, and the working oil port of the second control reversing valve 49 is connected to the rod chamber of the oil cylinder used to drive the brake to open.

[0078] The brake is used to brake the output shaft of the motor 100 .

[0079] The pressure reducing valve 47 is used to reduce the pressure of the control oil of the brake. The first control reversing valve 48 and the second control reversing valve 49 are used to control the opening or closing of the brake. When both electromagnetic reversing valves are energized, the control oil enters the brake and the brake is opened; when one of the first control reversing valve 48 and the second control reversing valve 49 loses power, the control oil is depressurized and the brake is automatically closed to improve safety.

[0080] Figure 7 yes Figure 1 The enlarged image of the upper left part of the middle, combined with Figure 7 Optionally, the test control system further includes a locking valve group 5, which further includes a locking shuttle valve 51, a locking electromagnetic reversing valve 52 and a locking cartridge valve 53. The first oil port of the locking shuttle valve 51 is respectively connected to the oil return port of the high-pressure check valve 41 and the oil inlet port of the locking cartridge valve 53, the second oil port of the locking shuttle valve 51 is connected to the first oil port of the motor 100, the oil return port of the locking shuttle valve 51 is connected to the oil inlet port of the locking electromagnetic reversing valve 52, the oil return port of the locking electromagnetic reversing valve 52 is connected to the oil tank, the working oil port of the locking electromagnetic reversing valve 52 is connected to the control oil port of the locking cartridge valve 53, and the oil return port of the locking cartridge valve 53 is connected to the first oil port of the motor 100.

[0081] In the above implementation, the locking valve assembly 5 is used to lock the motor 100 so that the motor 100 can be braked in an emergency.

[0082] The locking solenoid reversing valve 52 is used to control whether the locking cartridge valve 53 is open. The first oil port A of the locking shuttle valve 51 is connected to the oil return port of the high-pressure check valve 41, and the second oil port B of the locking shuttle valve 51 is connected to the first oil port A of the motor 100. The oil pressure of the oil return port C of the locking shuttle valve 51 is always the higher pressure of the first oil port A and the second oil port B. When the locking solenoid reversing valve 52 loses power, the locking cartridge valve 53 closes, locking the motor 100, making it impossible for the winch to reel in or release the rope. When the locking solenoid reversing valve 52 is energized, the locking cartridge valve 53 opens, allowing the motor 100 to rotate.

[0083] Optionally, the test control system further includes a safety valve group 6, which includes a safety cartridge valve 61, a first safety relief valve 62, a second safety relief valve 63 and a safety electromagnetic reversing valve 64;

[0084] The oil inlet of the safety cartridge valve 61 is connected to the oil return port of the locking cartridge valve 53, the first oil port of the motor 100 and the oil inlet of the safety first relief valve 62 respectively, and the oil return port of the safety cartridge valve 61 is connected to the second oil port of the motor 100 and the oil inlet of the low-pressure relief valve unit 44 respectively. The oil return port of the safety first relief valve 62 is connected to the oil tank, and the control oil port of the safety first relief valve 62 is connected to its own oil inlet. The oil inlet of the safety second relief valve 63 is connected to the working oil port of the safety electromagnetic reversing valve 64, the oil return port of the safety second relief valve 63 is connected to the oil tank, and the control oil port of the safety second relief valve 63 is connected to its own oil inlet. The oil inlet of the safety electromagnetic reversing valve 64 is connected to the control oil port of the safety cartridge valve 61 and the oil inlet of the safety first relief valve 62, and the oil return port of the safety electromagnetic reversing valve 64 is connected to the oil tank.

[0085] In the above implementation, when the safety electromagnetic reversing valve 64 loses power, the set pressure depends on the safety first overflow valve 62 ; when the safety electromagnetic reversing valve 64 is energized, the set pressure depends on the safety second overflow valve 63 .

[0086] In this embodiment, in order to further improve the response speed of the motor 100, the motor 100 is also connected to a forced large displacement valve 101, a high-frequency response valve 102 and a motor variable cylinder 103. The oil inlet P of the high-frequency response valve 102 is connected to the oil inlet A of the locking cartridge valve 53, the oil return port T of the high-frequency response valve 102 is connected to the second oil port B of the motor 100, and the first working oil port A and the second working oil port B of the high-frequency response valve 102 are respectively connected to the two oil inlets of the forced large displacement valve 101. The two oil return ports of the forced large displacement valve 101 are respectively connected to the two oil chambers of the motor variable cylinder 103. The other two oil inlets of the forced large displacement valve 101 are respectively connected to the second oil port B of the motor 100 and the oil return port C of the locking shuttle valve 51. The piston rod of the motor variable cylinder 103 is connected to the motor 100.

[0087] The following briefly introduces the working process of the control system provided by the embodiment of the present disclosure:

[0088] 1) Winch rope collection:

[0089] The first pump body 120 and the second pump body 220 are driven, the first electromagnetic reversing valve 32 and the second electromagnetic reversing valve 34 are energized, the first proportional pressure reducing valve 31 controls the set pressure of the first pump body 120, and the second proportional pressure reducing valve 33 controls the set pressure of the second pump body 220.

[0090] The high-pressure oil in the oil return port of the first pump body 120 passes through the high-pressure check valve 41 to reach the oil inlet A of the locking cartridge valve 53, the locking solenoid reversing valve 52 is energized, and the locking cartridge valve 53 is opened. The high-pressure oil reaches the first oil port A of the motor 100.

[0091] The high-pressure oil from the return port of the second pump body 220 directly reaches the second oil port B of the motor 100 through the low-pressure check valve 43. At this time, the pressure difference between the first oil port A and the second oil port B of the motor 100 is constant and depends on the set pressure difference between the first pump body 120 and the second pump body 220. Changing the displacement of the motor 100 can change the output torque of the motor 100.

[0092] The forced large displacement valve 101 of the motor 100 is energized, so that the high-frequency response valve 102 is connected to the motor variable cylinder 103. The high-frequency response valve 102 is controlled to change direction and the displacement of the motor 100 is changed through the motor variable cylinder 103, so that the output torque of the motor 100 is slightly greater than the load demand torque. At this time, the first control reversing valve 48 and the second control reversing valve 49 are energized, the control oil opens the brake, the first oil port A of the motor 100 enters oil, and the second oil port B returns oil, driving the winch to retract the rope.

[0093] 2) Winch rope release

[0094] The high-frequency response valve 102 is controlled to change direction and the displacement of the motor 100 is changed through the motor variable cylinder 103, so that the output torque of the motor 100 is slightly less than the load demand torque. At this time, the first control reversing valve 48 and the second control reversing valve 49 are energized, the control oil opens the brake, the second oil port B of the motor 100 enters oil, and the first oil port A returns oil. The motor 100 works in the pump working state, and the winch releases the rope.

[0095] 3) Motor 100 and winch emergency stop impact test

[0096] When the winch releases the rope, the system stops and the power is cut off, and the first pump body 120 and the second pump body 220 stop supplying oil. At this time, the large displacement valve 101 is forced to lose power, and the high-pressure oil at the oil return port C of the locking shuttle valve 51 directly enters the motor variable cylinder 103, so that the motor 100 becomes the maximum displacement to support the load. In addition, the first control reversing valve 48 and the second control reversing valve 49 lose power, the brake control oil is depressurized, and the brake is automatically closed to ensure safety.

[0097] The above description is only an optional embodiment of the present disclosure and is not intended to limit the present disclosure. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present disclosure shall be included in the protection scope of the present disclosure.

Claims

1. A test control system for a hydraulic motor, characterized in that: The test control system comprises a high-pressure pump group (1), a low-pressure pump group (2), a pressure regulating valve group (3), a control valve group (4) and a winch system (200); The control valve group (4) is respectively connected to the low-pressure pump group (2), the high-pressure pump group (1), the first oil port of the motor (100), and the second oil port of the motor (100). The control valve group (4) is configured to: deliver the oil pumped by the high-pressure pump group (1) to the first oil port of the motor (100), and recover the oil output from the second oil port of the motor (100) in the oil tank, so as to drive the motor (100) to rotate forward; or deliver the oil pumped by the low-pressure pump group (2) to the second oil port of the motor (100), and recover the oil output from the first oil port of the motor (100) in the oil tank, so as to drive the motor (100) to rotate reversely; The pressure regulating valve group (3) is connected to the high-pressure pump group (1) and the low-pressure pump group (2) respectively, and the pressure regulating valve group (3) is used to adjust the oil pressure of the oil pumped by the high-pressure pump group (1) at the first oil port of the motor (100) and to adjust the oil pressure of the oil pumped by the low-pressure pump group (2) at the second oil port of the motor (100), so that when the motor (100) rotates forward or reverse, the oil pressure at the first oil port of the motor (100) is greater than the oil pressure at the second oil port of the motor (100); The winch system (200) is connected to the motor (100).

2. The test control system according to claim 1, characterized in that: The high-pressure pump group (1) comprises a first motor (11), a first variable displacement pump unit (12) and a fixed displacement pump (13); The first motor (11) is connected to the first variable displacement pump unit (12) and the fixed displacement pump (13) respectively, and the oil return port of the first variable displacement pump unit (12) is connected to the control valve group (4); The first variable displacement pump unit (12) comprises a first pump body (120), a first variable displacement cylinder (121), a first shuttle valve (122), a first displacement control valve (123) and a first pressure control valve (124); The rod chamber of the first variable cylinder (121) is connected to the variable mechanism of the first pump body (120), the rodless chamber of the first variable cylinder (121) is connected to the working oil port of the first displacement control valve (123), the oil inlet of the first displacement control valve (123) is connected to the working oil port of the first pressure control valve (124), and the oil return port of the first displacement control valve (123) is connected to the oil tank; The first oil port of the first shuttle valve (122) is connected to the oil return port of the metering pump (13), and the second oil port of the first shuttle valve (122) is connected to the oil return port of the first pump body (120); The oil inlet of the first pressure control valve (124) is connected to the oil return port of the first shuttle valve (122), the oil return port of the first pressure control valve (124) is connected to the oil tank, the first control oil port of the first pressure control valve (124) is connected to the pressure regulating valve group (3), and the second control oil port of the first pressure control valve (124) is connected to the oil return port of the first shuttle valve (122).

3. The test control system according to claim 2, characterized in that: The pressure regulating valve group (3) comprises a first proportional pressure reducing valve (31) and a first electromagnetic reversing valve (32), wherein the oil inlet of the first proportional pressure reducing valve (31) is connected to the oil return port of the metering pump (13), the oil return port of the first proportional pressure reducing valve (31) is connected to the oil inlet of the first electromagnetic reversing valve (32), the control oil port of the first proportional pressure reducing valve (31) is connected to its own oil return port, and the oil drain port of the first proportional pressure reducing valve (31) is connected to the oil tank; The working oil port of the first electromagnetic reversing valve (32) is connected to the first control oil port of the first pressure control valve (124), and the oil return port of the first electromagnetic reversing valve (32) is connected to the oil tank.

4. The test control system according to claim 3, characterized in that: The low-pressure pump group (2) comprises a second motor (21) and a second variable pump unit (22), the second motor (21) is connected to the second variable pump unit (22), and the oil return port of the second variable pump unit (22) is connected to the control valve group (4); The pressure regulating valve group (3) further comprises a second proportional pressure reducing valve (33) and a second electromagnetic reversing valve (34), wherein the oil inlet of the second proportional pressure reducing valve (33) is connected to the oil return port of the metering pump (13), the oil return port of the second proportional pressure reducing valve (33) is connected to the oil inlet of the second electromagnetic reversing valve (34), and the control oil port of the second proportional pressure reducing valve (33) is connected to its own oil return port; The working oil port of the second electromagnetic reversing valve (34) is connected to the second variable pump unit (22), and the oil return port of the second electromagnetic reversing valve (34) is connected to the oil tank.

5. The test control system according to claim 4, characterized in that: The pressure regulating valve group (3) further comprises a control oil overflow valve (35), the oil inlet of the control oil overflow valve (35) being respectively connected to the oil return port of the metering pump (13) and the first oil port of the first shuttle valve (122), the oil return port of the control oil overflow valve (35) being connected to the oil tank, and the control oil port of the control oil overflow valve (35) being connected to its own oil inlet.

6. The test control system according to any one of claims 1 to 5, characterized in that: The control valve group (4) comprises a high-pressure check valve (41), a high-pressure relief valve unit (42), a low-pressure check valve (43) and a low-pressure relief valve unit (44); The oil inlet of the high-pressure one-way valve (41) is connected to the oil return port of the high-pressure pump group (1), the oil return port of the high-pressure one-way valve (41) is connected to its own hydraulic control port, and the oil return port of the high-pressure one-way valve (41) is connected to the first oil port of the motor (100); The oil inlet of the high-pressure relief valve unit (42) is respectively connected to the oil return port of the high-pressure check valve (41) and the first oil port of the motor (100), and the oil return port of the high-pressure relief valve unit (42) is respectively connected to the oil inlet of the low-pressure relief valve unit (44), the second oil port of the motor (100) and the oil return port of the low-pressure check valve (43). The high-pressure relief valve unit (42) is configured such that when the oil pressure of the oil at the oil inlet of the high-pressure relief valve unit (42) is higher than a first threshold value, the oil flowing into the oil inlet of the high-pressure relief valve unit (42) is discharged from the oil return port of the high-pressure relief valve unit (42); The oil inlet of the low-pressure one-way valve (43) is connected to the oil return port of the low-pressure pump group (2), and the hydraulic control port of the low-pressure one-way valve (43) is connected to its own oil return port; The oil return port of the low-pressure relief valve unit (44) is connected to the oil tank, and the low-pressure relief valve unit (44) is configured such that when the oil pressure of the oil at the oil inlet of the low-pressure relief valve unit (44) is higher than a second threshold value, the oil flowing into the oil inlet of the low-pressure relief valve unit (44) is discharged from the oil return port of the low-pressure relief valve unit (44), and the first threshold value is greater than the second threshold value.

7. The test control system according to claim 6, characterized in that: The high-pressure relief valve unit (42) comprises a first control check valve (421) and a first control relief valve (422), wherein the oil inlet of the first control check valve (421) is respectively connected to the first oil port of the motor (100) and the oil return port of the high-pressure check valve (41), and the oil return port of the first control check valve (421) is respectively connected to the oil return port of the first control relief valve (422), the oil inlet of the low-pressure relief valve unit (44), the oil return port of the low-pressure check valve (43), and the second oil port of the motor (100); The control oil port of the first control check valve (421) is connected to the oil inlet of the first control overflow valve (422), and the control oil port of the first control overflow valve (422) is connected to its own oil inlet.

8. The test control system according to claim 7, characterized in that: The control valve group (4) further comprises a total control overflow valve (46), the oil inlet of the total control overflow valve (46) being respectively connected to the first oil port of the motor (100) and the oil inlet of the first control check valve (421), the oil return port of the total control overflow valve (46) being connected to the oil tank, and the control oil port of the total control overflow valve (46) being connected to its own oil inlet.

9. The test control system according to claim 6, characterized in that: The test control system further comprises a locking valve group (5), wherein the locking valve group (5) further comprises a locking shuttle valve (51), a locking electromagnetic reversing valve (52) and a locking cartridge valve (53). The first oil port of the locking shuttle valve (51) is respectively connected to the oil return port of the high-pressure check valve (41) and the oil inlet port of the locking cartridge valve (53); the second oil port of the locking shuttle valve (51) is connected to the first oil port of the motor (100); the oil return port of the locking shuttle valve (51) is connected to the oil inlet port of the locking electromagnetic reversing valve (52); the oil return port of the locking electromagnetic reversing valve (52) is connected to the oil tank; the working oil port of the locking electromagnetic reversing valve (52) is connected to the control oil port of the locking cartridge valve (53); and the oil return port of the locking cartridge valve (53) is connected to the first oil port of the motor (100).

10. The test control system according to claim 9, characterized in that: The test control system further comprises a safety valve group (6), wherein the safety valve group (6) comprises a safety cartridge valve (61), a first safety overflow valve (62), a second safety overflow valve (63) and a safety electromagnetic reversing valve (64); The oil inlet of the safety cartridge valve (61) is respectively connected to the oil return port of the locking cartridge valve (53), the first oil port of the motor (100) and the oil inlet of the safety first relief valve (62); the oil return port of the safety cartridge valve (61) is respectively connected to the second oil port of the motor (100) and the oil inlet of the low-pressure relief valve unit (44); The oil return port of the first safety relief valve (62) is connected to the oil tank, and the control oil port of the first safety relief valve (62) is connected to its own oil inlet; The oil inlet of the second safety overflow valve (63) is connected to the working oil port of the safety electromagnetic reversing valve (64), the oil return port of the second safety overflow valve (63) is connected to the oil tank, and the control oil port of the second safety overflow valve (63) is connected to its own oil inlet; The oil inlet of the safety electromagnetic reversing valve (64) is connected to the control oil port of the safety cartridge valve (61) and the oil inlet of the safety first overflow valve (62), and the oil return port of the safety electromagnetic reversing valve (64) is connected to the oil tank.

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