A test bench and test method integrating running-in and parameter measurement

Abstract

The present invention relates to a test bench that integrates running-in and parameter measurement, comprising a test bench, and a mounting plate that is adjustable in position and provided on one side of the test bench for mounting the equipment under test; further comprising a static torque detection component and a passive hydraulic component for balancing the output torque of the equipment under test, which are respectively installed on the test bench and connected to the equipment under test, and a PLC control system. The test bench of the present invention has no active power of its own, and adopts the principle of small hole damping of the circulating fluid system to achieve dynamic balance with the equipment under test, thereby running in and measuring the parameters of the equipment under test. It has the characteristics of passive and flexible energy consumption, and has a simple structure, compact size, and easy operation. The working process is low in wear and low in noise, and has good use effect. The present invention also relates to a test bench test method.

Description

Technical Field

[0001] The present invention relates to the technical field of running-in test benches, and in particular to a test bench integrating running-in and parameter measurement. The present invention also relates to a test bench test method. Background Art

[0002] In the prior art, test platforms for testing performance parameters such as dynamic and static torque of power components of tested equipment or conducting power component running-in usually use active power systems such as motors as test power sources to balance the torque output of the power components. This use of active power systems as test power sources to balance the torque output of the power components often results in many shortcomings such as a large test platform, high energy consumption during the test process, and high test noise. For example, a motor is used to drive the brake disc to rotate to balance the output torque of the power component. During the test process, not only is there high motor energy consumption and a large test platform footprint, but also serious noise and dust pollution will be generated during the test due to the wear of the brake disc. At the same time, the brake shoes of the brake disc, as consumable parts, need to be replaced frequently, resulting in low economy and environmental adaptability. Summary of the Invention

[0003] In order to solve the above problems, the present invention provides a test bench that integrates running-in and parameter measurement. The test bench itself has no active power, and adopts the small hole damping principle of the circulating liquid system to achieve dynamic balance with the equipment under test, and then performs running-in and parameter measurement on the equipment under test. It has the characteristics of passive and flexible energy consumption, and has a simple structure, compact size, easy operation, low wear and low noise during the working process, and has good use effect.

[0004] The technical solution adopted by the present invention is: a test bench integrating running-in and parameter measurement, including a test bench and a mounting plate with an adjustable position arranged on one side of the test bench for mounting the equipment under test; also including a static torque detection component and a passive hydraulic component for balancing the output torque of the equipment under test, which are respectively installed on the test bench and connected to the equipment under test through transmission, and a PLC control system, the static torque detection component includes a connecting seat that meshes with the gear of the equipment under test via internal teeth, and a torque sensor installed on the connecting seat at one end; also including a static torque bracket movable assembly connected to the other end of the torque sensor, and a support seat installed on the test bench, the other end of the static torque bracket movable assembly passes through the support seat and is set in a free state, the static torque detection component also includes a torque wrench connected to one end of the free state setting of the static torque bracket movable assembly, and one end abuts against the torque wrench and the other end The power component installed on the test bench, the passive hydraulic component for balancing the output torque of the tested equipment includes a hydraulic box and a circulating fluid system connected to the hydraulic box, one end of the outlet of the circulating fluid system is connected to an oil suction filter; it also includes a hydraulic bridge connected to the circulating fluid system, and a three-position two-way solenoid valve adjacent to the hydraulic bridge and connected to the circulating fluid system, and also includes a proportional overflow valve, an electromagnetic flowmeter and a heat dissipation component connected in sequence to the circulating fluid system, a pressure gauge and a pressure sensor are connected to the circulating fluid system between the three-position two-way solenoid valve and the proportional overflow valve via a three-way pipeline, the hydraulic bridge includes a plunger pump connected to the tested equipment through a speed increaser, and a forward oil circuit connected to the plunger pump; it also includes a reverse oil circuit connected to the plunger pump, and a zero-load oil circuit connected between the three-position two-way solenoid valve and the hydraulic box.

[0005] As a further limitation of the above technical solution, the forward oil circuit includes a first one-way valve connected between the plunger pump and the oil suction filter, and a second one-way valve on the circulating fluid circuit system connected between the plunger pump and the three-position two-way solenoid valve; the reverse oil circuit includes a first reverse oil section with one end connected between the oil suction filter and the first one-way valve and the other end connected between the plunger pump and the second one-way valve, and a third one-way valve connected to the first reverse oil section, and also includes a second reverse oil section with one end connected between the first one-way valve and the plunger pump and the other end connected between the second one-way valve and the three-position two-way solenoid valve, and a fourth one-way valve connected to the second reverse oil section.

[0006] As a further limitation of the above technical solution, a torque and speed sensor is connected between the equipment under test and the speed increaser.

[0007] As a further limitation of the above technical solution, the heat dissipation component includes an oil temperature heat dissipation pipeline installed on the circulating liquid system, and a cooling fan arranged adjacent to the oil temperature heat dissipation pipeline and connected to the PLC control system via electrical signals; it also includes an oil temperature sensor and an oil level sensor arranged in the hydraulic box and connected to the PLC control system via electrical signals.

[0008] As a further limitation of the above technical solution, a pressure pipeline filter is connected to the circulating liquid system between the three-position two-way solenoid valve and the three-way pipeline.

[0009] As a further limitation of the above technical solution, the static torque support movable assembly includes a sliding seat connected to the torque sensor at one end and having an external hexagonal mounting surface at the other end, and a friction-reducing bushing sleeved between the sliding seat and the support seat; and also includes a locking nut for axially limiting the sliding seat, the friction-reducing bushing and the support seat.

[0010] As a further limitation of the above technical solution, the friction-reducing bushing is a copper bushing, and the cross section of the friction-reducing bushing is T-shaped, and a support ring is installed between the step surface of the support seat and the sliding seat.

[0011] As a further limitation of the above technical solution, the support seat includes an L-shaped body and a frustum formed on the body for the sliding seat to pass through, and one end of the frustum is in contact with the support ring.

[0012] As a further limitation of the above technical solution, the torque wrench has an arc surface on one end thereof that abuts against the power assembly, and the power assembly includes a jack.

[0013] The present invention provides a test bench that integrates running-in and parameter measurement. Through the arrangement of a static torque detection component, a passive hydraulic component for balancing the output torque of the equipment under test, and a PLC control system, the test bench itself has no active power and adopts the small hole damping principle of the circulating fluid system to achieve dynamic balance with the equipment under test, thereby performing running-in and parameter measurement on the equipment under test. The test bench has the characteristics of passiveness and flexible energy consumption, and has a simple structure, compact size, easy operation, low wear and low noise during the working process, and has good use effect.

[0014] The present invention also relates to a test bench test method, which is performed using the aforementioned test bench integrating running-in and parameter measurement, and includes the following method:

[0015] a. Run-in method

[0016] a1. Connecting the output shaft of the equipment under test to the speed increaser, and performing a running-in operation by using a passive hydraulic component to achieve dynamic balancing of the output torque of the equipment under test;

[0017] a11. Connecting the motor of the equipment under test to the PLC control system, and adjusting the motor via the PLC control system to change the power parameters of the equipment under test as needed;

[0018] a12. The output shaft of the equipment under test is connected to the speed increaser to achieve power transmission of the equipment under test;

[0019] a13. The output torque of the equipment under test is balanced by the hydraulic resistance of the forward oil circuit of the passive hydraulic component to achieve dynamic balance of the output torque of the equipment under test, and then run-in is performed.

[0020] b. Parameter measurement method

[0021] b1. Engaging the gear of the equipment under test with the internal teeth of the connecting base, starting the equipment under test, and vertically increasing the abutting end of the torque wrench via the power assembly, thereby applying a rotational force to the static torque support movable assembly until the static torque support movable assembly rotates relative to the support base. When the torque sensor measures a maximum value, the upward movement of the torque wrench is stopped. The maximum value measured by the torque sensor is the desired signal, thereby measuring the static torque of the equipment under test;

[0022] b2. In step a1, the passive hydraulic assembly is used to achieve a dynamic balance of the output torque of the equipment under test, and the required parameters are measured by the electromagnetic flowmeter, pressure gauge and pressure sensor. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 This is a schematic diagram of the assembly structure of a test bench integrating running-in and parameter measurement according to the present invention;

[0024] Figure 2 This is a schematic diagram of the assembly structure from another angle of a test bench integrating running-in and parameter measurement of the present invention;

[0025] Figure 3 This is a schematic diagram of the third angle assembly structure of a test bench integrating running-in and parameter measurement of the present invention;

[0026] Figure 4 This is a hydraulic system diagram of a passive hydraulic assembly for output torque balancing of the equipment under test according to the present invention;

[0027] Figure 5A partial structural diagram of a passive hydraulic assembly for output torque balancing of the equipment under test according to the present invention;

[0028] Figure 6 It is a control principle diagram of the PLC control system of the present invention;

[0029] Figure 7 A partial structural cross-sectional view of a static moment detection assembly of the present invention;

[0030] Figure 8 It is a structural schematic diagram of the support base of the present invention;

[0031] Figure 9 It is a structural schematic diagram of the static moment bracket movable assembly of the present invention;

[0032] Figure 10 It is a structural schematic diagram of the torque wrench of the present invention.

[0033] In the picture:

[0034] 1-bench, 2-mounting plate, 21-mounting hole, 22-through hole, 3-static torque detection assembly, 31-connecting seat, 311-internal gear, 32-torque sensor, 33-static torque bracket movable assembly, 331-sliding seat, 332-friction reducing bushing, 333-locking nut, 334-support ring, 335-first step surface, 336-second step surface, 337-third step surface, 338-external hexagonal mounting surface, 34-support seat, 341-body, 342-round table, 35-torque wrench, 351-arc surface, 36-power assembly, 4-gear, 5-tested equipment, 6-passive hydraulic assembly for output torque balancing of the tested equipment, 61-hydraulic box, 62-circulating fluid system System, 63-Oil suction filter, 64-Hydraulic bridge, 641-Speed ​​increaser, 642-Plunger pump, 6431-First one-way valve, 6432-Second one-way valve, 6441-First reversing oil section, 6442-Third one-way valve, 6443-Second reversing oil section, 6444-Fourth one-way valve, 645-Zero load oil circuit, 65-Three-position two-way solenoid valve, 66-Proportional relief valve, 67-Electromagnetic flowmeter, 68-Heating assembly, 681-Oil temperature cooling pipeline, 682-Cooling fan, 683-Oil temperature sensor, 684-Oil level sensor, 69-Pressure gauge, 610-Pressure sensor, 611-Pressure line filter, 612-Torque and speed sensor, 7-PLC control system. DETAILED DESCRIPTION

[0035] The present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0036] Example 1

[0037] A test bench that integrates running-in and parameter measurement, consisting of Figures 1 to 3 As shown in the figure, it includes a stand 1, and a mounting plate 2 with an adjustable position provided on one side of the stand 1 for mounting the equipment under test 5; it also includes a static torque detection component 3 and a passive hydraulic component 6 for output torque balancing of the equipment under test, which are respectively installed on the stand 1 and are transmission-connected to the equipment under test 5, and a PLC control system 7. Specifically, the mounting plate 2 is slidably provided on one side of the stand 1 to adjust the position of the mounting plate 2 accordingly. To facilitate the installation of different equipment under test 5, a plurality of mounting holes 21 and through holes 22 are provided on the mounting plate 2. By adjusting the position of the mounting plate 2 so that the through holes 22 are aligned with the static torque detection component 3 or the passive hydraulic component 6 for output torque balancing of the equipment under test, the connection between the equipment under test 5 and the aforementioned two is completed.

[0038] Depend on Figure 1 Combine Figures 7 to 10 As shown in the figure, the static torque detection component 3 includes a connecting seat 31 that is meshed with the gear 4 of the measured equipment 5 via the internal teeth 311, and a torque sensor 32 with one end mounted on the connecting seat 31; it also includes a static torque bracket movable assembly 33 connected to the other end of the torque sensor 32, and a support seat 34 mounted on the test bench 1, the other end of the static torque bracket movable assembly 33 passes through the support seat 34 and is set in a free state, the static torque detection component 3 also includes a torque wrench 35 connected to one end of the free state setting of the static torque bracket movable assembly 33, and a power component 36 with one end resting on the torque wrench 35 and the other end mounted on the test bench 1.

[0039] The power component 36 pushes the abutting end of the torque wrench 35 to rise in the vertical direction, and applies a rotational force to the static torque bracket movable assembly 33 until the static torque bracket movable assembly 33 rotates relative to the support seat 34. The maximum value measured by the torque sensor 32 is the required signal, realizing automatic detection of the static torque of the measured equipment 5, with a simple structure and high measurement accuracy.

[0040] Specifically, in order to prevent the torque wrench 35 and the power assembly 36 from being offset relative to each other when the power assembly 36 applies a vertical thrust to the torque wrench 35, Figure 10 As shown in FIG, the torque wrench 35 has an arc surface 351 on one end thereof which abuts against the power assembly 36. To simplify the structure and facilitate operation, the power assembly 36 includes a jack.

[0041] Depend on Figure 7As shown in the figure, the static torque support movable assembly 33 includes a sliding seat 331 with one end connected to the torque sensor 32 and the other end formed with an external hexagonal mounting surface 338, and a friction-reducing bushing 332 arranged between the sliding seat 331 and the support seat 34; it also includes a locking nut 333 for axially limiting the sliding seat 331, the friction-reducing bushing 332 and the support seat 34. Specifically, a bolt mounting hole 21 is provided at one end of the sliding seat 331, and the end is connected to the torque sensor 32 via a bolt. An outer hexagonal mounting surface 338 is formed at the other end of the sliding seat 331, which is convenient for fitting with the inner hexagonal sleeve of the torque wrench 35. In order to facilitate the installation of the locking nut 333 and the support ring 334 described below, a three-step surface is formed on the outer surface of the sliding seat 331. In this embodiment, the friction-reducing bushing 332 is a copper bushing, and the cross section of the friction-reducing bushing 332 is T-shaped. A support ring 334 is installed between the step surfaces of the support seat 34 and the sliding seat 331, that is, Figure 7 Combine Figure 9 As shown in the figure, a support ring 334 is installed between the third step surface 337 and the second step surface 336 at one end adjacent to the sliding seat 331 where the bolt mounting hole 21 is opened, and a locking nut 333 is installed between the second step surface 336 and the first step surface 335.

[0042] Depend on Figure 8 As shown in FIG, the support seat 34 includes an L-shaped body 341 and a truncated platform 342 formed on the body 341 for the sliding seat 331 to pass through. One end of the truncated platform 342 contacts the support ring 334.

[0043] Depend on Figure 1 、 Figure 3 、 Figure 4 Combine Figure 6As shown in the figure, the passive hydraulic assembly 6 for output torque balancing of the tested equipment includes a hydraulic box 61, and a circulating fluid system 62 connected to the hydraulic box 61, one end of the outlet of the circulating fluid system 62 is connected to an oil suction filter 63; it also includes a hydraulic bridge 64 connected to the circulating fluid system 62, and a three-position two-way solenoid valve 65 adjacent to the hydraulic bridge 64 and connected to the circulating fluid system 62, and also includes a proportional relief valve 66 and an electromagnetic flowmeter connected in sequence to the circulating fluid system 62. 67 and heat dissipation assembly 68. A pressure gauge 69 and a pressure sensor 610 are connected to the circulating fluid system 62 between the three-position, two-way solenoid valve 65 and the proportional relief valve 66 via a three-way pipeline. The hydraulic bridge circuit 64 includes a plunger pump 642, which is transmission-connected to the device under test 5 via a speed increaser 641, and a forward oil circuit connected to the plunger pump 642; it also includes a reverse oil circuit connected to the plunger pump 642, and a zero-load oil circuit 645 connected between the three-position, two-way solenoid valve 65 and the hydraulic tank 61. A torque and speed sensor 612 is connected between the device under test 5 and the speed increaser 641. Specifically, the speed increaser 641 can be in the form of an inverted reducer.

[0044] Specifically, by adjusting the proportional relief valve 66, the flow rate of the hydraulic bridge 64 can be adjusted, and the flow rate is measured by the electromagnetic flowmeter 67 to match the parameters of the equipment under test 5. During the process, the pressure value is measured by the pressure gauge 69 and the pressure sensor 610, and the power and other parameters are measured comprehensively by the flow and pressure. In the absence of an external power source, the torque, speed, pressure, power, efficiency and other parameters of the equipment under test 5 can be measured through the passive hydraulic component, or the running-in test of the equipment under test 5 can be achieved through the passive hydraulic component. The structure is simple, the operation is convenient, and it will not cause wear to the power components of the equipment under test 5, and has a good use effect.

[0045] Depend on Figure 4As shown in the figure, the forward oil circuit includes a first one-way valve 6431 connected between the plunger pump 642 and the oil suction filter 63, and a second one-way valve 6432 on the circulating fluid system 62 connected between the plunger pump 642 and the three-position two-way solenoid valve 65; the reverse oil circuit includes a first reverse oil section 6441 connected at one end between the oil suction filter 63 and the first one-way valve 6431 and at the other end between the plunger pump 642 and the second one-way valve 6432, and a third one-way valve 6442 connected to the first reverse oil section 6441; and also includes a second reverse oil section 6443 connected at one end between the first one-way valve 6431 and the plunger pump 642 and at the other end between the second one-way valve 6432 and the three-position two-way solenoid valve 65, and a fourth one-way valve 6444 connected to the second reverse oil section 6443. When rotating forward, the oil flows through the first one-way valve 6431, the circulating fluid system 62, the plunger pump 642, and the second one-way valve 6432. When reversing is required, the oil flows through the first reversal oil section 6441, the third one-way valve 6442, the plunger pump 642, the second reversal oil section 6443, the fourth one-way valve 6444, and the circulating fluid system 62.

[0046] In this embodiment, a pressure line filter 611 is connected to the circulating liquid system 62 between the three-position two-way solenoid valve 65 and the three-way pipeline. A switch connected in parallel with the pressure line filter 611 is connected to the circulating liquid system 62. When the pressure difference between the two sides of the pressure line filter 611 is greater than 0.35 MPa, the PLC control system 7 controls the switch to open, that is, Figure 4 The value of P1 minus P2 is greater than 0.35MPa.

[0047] To facilitate heat dissipation, the heat dissipation component 68 includes an oil temperature heat dissipation pipeline 681 installed on the circulating liquid system 62, and a cooling fan 682 arranged adjacent to the oil temperature heat dissipation pipeline 681 and connected to the PLC control system 7 via electrical signals; it also includes an oil temperature sensor 683 and an oil level sensor 684 arranged in the hydraulic box 61 and connected to the PLC control system 7 via electrical signals.

[0048] Example 2

[0049] This embodiment relates to a test bench test method, which is performed using the test bench that integrates running-in and parameter measurement in the first embodiment, and includes the following methods:

[0050] a. Run-in method

[0051] a1. Connect the output shaft of the equipment under test 5 to the speed increaser 641, and use the passive hydraulic assembly 6 to achieve dynamic balance of the output torque of the equipment under test 5, thereby performing running-in.

[0052] a11. Connect the motor of the equipment under test 5 to the PLC control system 7, and adjust the motor via the PLC control system 7 to change the power parameters of the equipment under test 5 as needed;

[0053] a12. The output shaft of the device under test 5 is connected to the speed increaser 641 to achieve power transmission of the device under test 5;

[0054] a13. The output torque of the equipment under test 5 is balanced by the hydraulic resistance of the positive oil circuit of the passive hydraulic assembly 6 to achieve dynamic balance of the output torque of the equipment under test 5 and perform running-in.

[0055] Specifically, in step a11, the tested equipment 5 can be connected to the control box of the test bench during the test (the control box is electrically connected to the PLC control system 7), and the Figure 5 As shown in , the relay contactor is turned on through the DI output of the PLC control system 7, thereby turning on the motor of the equipment under test 5. At the same time, the driver of the motor of the equipment under test 5 is adjusted through the DO output of the PLC, thereby adjusting the driving current of the motor of the equipment under test 5 to change the power parameters of the equipment under test 5 as needed.

[0056] In step a12 , the equipment under test 5 is coupled to the test bench via the mounting plate 2 , so as to transmit the power output of the equipment under test 5 to the test bench.

[0057] b. Parameter measurement method

[0058] b1. Engage the gear 4 of the equipment under test 5 with the internal teeth 311 of the connecting base 31, start the equipment under test 5, and use the power assembly 36 to push the abutting end of the torque wrench 35 upward in the vertical direction, thereby applying a rotational force to the static torque bracket movable assembly 33 until the static torque bracket movable assembly 33 rotates relative to the support base 34. When the torque sensor 32 measures a maximum value, stop pushing the torque wrench 35 upward. The maximum value measured by the torque sensor 32 is the required signal, thereby measuring the static torque of the equipment under test 5;

[0059] b2. In step a1, the passive hydraulic assembly 6 is used to achieve a dynamic balance of the output torque of the equipment under test 5 by balancing the output torque of the equipment under test, and the required parameters are measured by the electromagnetic flowmeter 67, the pressure gauge 69 and the pressure sensor 610.

[0060] In step b2, since a torque and speed sensor 612 is connected between the equipment under test 5 and the speed increaser 641, the speed and torque of the equipment under test 5 at this time can be measured, and the actual speed and torque inside the equipment under test 5 can be obtained by converting the system transmission ratio. In this embodiment, the torque and speed sensor 612 is connected to other components of the test bench through a universal joint, which can improve the stability of the test when the test bench is not concentric. The setting of the speed increaser 641 can reduce the torque and increase the speed, and transmit the increased speed output power to the plunger pump 642 through the vertical steering mechanism and the universal joint, and drive the rotor of the plunger pump 642 to rotate. The purpose of its speed increase is to meet the minimum speed requirement of the plunger pump 642, thereby achieving stable pumping of liquid by the plunger pump 642.

[0061] The power output of the equipment under test 5 is mechanically transmitted, driving the rotation of the plunger pump 642. This pump is a fixed-displacement pump, and its flow rate is positively correlated with the rotational speed, independent of the pressure. A hydraulic bridge 64 is provided at the inlet and outlet of the plunger pump 642, ensuring that regardless of the direction of the power output of the equipment under test 5, the plunger pump 642 can pump fluid to the rear-end circulating fluid system 62 through the hydraulic bridge 64.

[0062] The circulating fluid system 62 is connected to a proportional relief valve 66. Adjusting the proportional relief valve 66 to reduce its opening increases the oil pressure in the circulating fluid system 62. Since the selected plunger pump 642 is a fixed-displacement pump, the flow rate remains constant under the premise of constant speed. Increasing the oil pressure increases the load resistance. When the power output torque of the tested equipment 5 is balanced with the load resistance, the speed of the passive hydraulic assembly 6 for output torque balancing of the tested equipment remains unchanged. At this time, the test performance parameters are obtained through the aforementioned sensors, and the relevant test conclusions are drawn through the algorithm within the PLC control system 7. The details are as follows:

[0063] A. Input power of the tested power component 36:

[0064] P 1入 =UI, where U is the input voltage of the motor of the equipment under test 5, and I is the input current of the motor of the equipment under test 5.

[0065] This parameter is measured by the external motor driver / inverter and input into the PLC control system 7 through the 485 serial port for internal calculation;

[0066] B. Speed, torque and direct output power of the equipment under test 5:

[0067] P 1出 =Tn, where T is the torque of the equipment under test 5, and n is the speed of the passive hydraulic assembly used to balance the output torque of the equipment under test 5;

[0068] T is measured by the torque speed sensor 612;

[0069] C. The pressure, flow and balance power measured by the passive hydraulic component 6 for output torque balance of the tested equipment:

[0070] P2=Qp, where Q is the flow rate, which can be measured by the electromagnetic flowmeter 67, and p is the oil pressure, which can be measured by the installed oil pressure sensor.

[0071] D. The efficiency of the equipment under test 5 and the output torque balance of the equipment under test are calibrated using the working efficiency of the passive hydraulic component 6:

[0072] Efficiency of the tested equipment 5: η1=P 1出 / P 1入 ;

[0073] Working efficiency of the passive hydraulic component 6 used to balance the output torque of the tested equipment: η2=P2 / P 1出 .

[0074] The above description is only a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any technical solution obtained by any technician familiar with the field within the technical scope disclosed by the present invention and by equivalent replacement or modification based on the technical concept of the present invention should be covered by the scope of protection of the present invention.

Claims

1. A test bench integrating running-in and parameter measurement, characterized by: The device comprises a stand and a mounting plate which is adjustable in position and is provided on one side of the stand for mounting the equipment under test; the device also comprises a static torque detection component which is respectively installed on the stand and is transmission-connected to the equipment under test and a passive hydraulic component for output torque balancing of the equipment under test, and a PLC control system, the static torque detection component comprises a connecting seat which is meshed with the gear of the equipment under test via internal teeth, and a torque sensor which is installed at one end on the connecting seat; the device also comprises a static torque bracket movable assembly which is connected to the other end of the torque sensor, and a support seat which is installed on the stand, the other end of the static torque bracket movable assembly passes through the support seat and is set in a free state, the static torque detection component also comprises a torque wrench which is connected to one end of the free state setting of the static torque bracket movable assembly, and a power component which has one end resting on the torque wrench and the other end mounted on the stand. The passive hydraulic component for balancing the output torque of the equipment under test includes a hydraulic box and a circulating fluid system connected to the hydraulic box, one end of the outlet of the circulating fluid system is connected to an oil suction filter; it also includes a hydraulic bridge connected to the circulating fluid system, and a three-position two-way solenoid valve adjacent to the hydraulic bridge and connected to the circulating fluid system, and also includes a proportional overflow valve, an electromagnetic flowmeter and a heat dissipation component connected in sequence to the circulating fluid system, and a pressure gauge and a pressure sensor are connected to the circulating fluid system between the three-position two-way solenoid valve and the proportional overflow valve via a three-way pipeline. The hydraulic bridge includes a plunger pump connected to the equipment under test via a speed increaser, and a forward oil circuit connected to the plunger pump; it also includes a reverse oil circuit connected to the plunger pump, and a zero-load oil circuit connected between the three-position two-way solenoid valve and the hydraulic box.

2. The test bench integrating running-in and parameter measurement according to claim 1, characterized in that: The forward oil circuit includes a first one-way valve connected between the plunger pump and the oil suction filter, and a second one-way valve on the circulating fluid circuit system connected between the plunger pump and the three-position two-way solenoid valve; the reverse oil circuit includes a first reverse oil section with one end connected between the oil suction filter and the first one-way valve and the other end connected between the plunger pump and the second one-way valve, and a third one-way valve connected to the first reverse oil section, and also includes a second reverse oil section with one end connected between the first one-way valve and the plunger pump and the other end connected between the second one-way valve and the three-position two-way solenoid valve, and a fourth one-way valve connected to the second reverse oil section.

3. The test bench integrating running-in and parameter measurement according to claim 1, characterized in that: A torque and speed sensor is connected between the equipment under test and the speed increaser.

4. The test bench integrating running-in and parameter measurement according to claim 1, characterized in that: The heat dissipation component includes an oil temperature heat dissipation pipeline installed on the circulating liquid system, and a heat dissipation fan arranged adjacent to the oil temperature heat dissipation pipeline and connected to the PLC control system via electrical signals; it also includes an oil temperature sensor and an oil level sensor arranged in the hydraulic box and connected to the PLC control system via electrical signals.

5. The test bench integrating running-in and parameter measurement according to claim 1, characterized in that: A pressure pipeline filter is connected to the circulating fluid system between the three-position two-way solenoid valve and the three-way pipeline.

6. The test bench integrating running-in and parameter measurement according to claim 1, characterized in that: The static torque support movable assembly includes a sliding seat with one end connected to the torque sensor and the other end formed with an external hexagonal mounting surface, and a friction-reducing bushing sleeved between the sliding seat and the support seat; it also includes a locking nut for axially limiting the sliding seat, the friction-reducing bushing and the support seat.

7. The test bench integrating running-in and parameter measurement according to claim 6, characterized in that: The friction-reducing bushing is a copper bushing, and the cross section of the friction-reducing bushing is T-shaped. A support ring is installed between the support seat and the step surface of the sliding seat.

8. The test bench integrating running-in and parameter measurement according to claim 7, characterized in that: The support seat includes an L-shaped body and a truncated table formed on the body for the sliding seat to pass through, and one end of the truncated table is in contact with the support ring.

9. The test bench integrating running-in and parameter measurement according to claim 6, characterized in that: An arc surface is provided on one end of the torque wrench that abuts against the power assembly, and the power assembly includes a jack.

10. A test bench test method, performed using a test bench integrating running-in and parameter measurement according to any one of claims 1 to 9, characterized in that: The following methods are included: a. Run-in method a1. Connecting the output shaft of the equipment under test to the speed increaser, and performing a running-in operation by using a passive hydraulic component to achieve dynamic balancing of the output torque of the equipment under test; a11. Connecting the motor of the equipment under test to the PLC control system, and adjusting the motor via the PLC control system to change the power parameters of the equipment under test as needed; a12. The output shaft of the equipment under test is connected to the speed increaser to achieve power transmission of the equipment under test; a13. Balancing the output torque of the equipment under test by using the hydraulic resistance of the forward oil circuit of the passive hydraulic assembly to achieve dynamic balance of the output torque of the equipment under test, thereby performing running-in. b. Parameter measurement method b1. Engaging the gear of the equipment under test with the internal teeth of the connecting base, starting the equipment under test, and vertically increasing the abutting end of the torque wrench via the power assembly, thereby applying a rotational force to the static torque support movable assembly until the static torque support movable assembly rotates relative to the support base. When the torque sensor measures a maximum value, the upward movement of the torque wrench is stopped. The maximum value measured by the torque sensor is the desired signal, thereby measuring the static torque of the equipment under test; b2. In step a1, the passive hydraulic assembly is used to achieve a dynamic balance of the output torque of the equipment under test, and the required parameters are measured by the electromagnetic flowmeter, pressure gauge and pressure sensor.

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