A testing device for a high-pressure oil pump

Abstract

The application discloses a kind of test device of high-pressure oil pump, comprising: test system, test system includes servo motor, servo motor can drive high-pressure oil pump high-speed rotation, sealing mechanism is arranged between servo motor and high-pressure oil pump, sealing mechanism includes three-stage sealing assembly, three-stage sealing assembly can gradually increase pressure loss, the front end of high-pressure oil pump is sealed;Oil circuit system, oil circuit system includes multiple groups of conveying oil circuit, conveying oil circuit is connected with the first pump port or the second pump port of high-pressure oil pump, multiple groups of conveying oil circuit are all provided with check valve, by adjusting check valve, the oil inlet and oil outlet state of the first pump port and the second pump port of high-pressure oil pump can be switched, the performance test under the working condition of high-pressure oil pump forward rotation and reverse rotation is realized. By the cooperation design of sealing assembly, conveying oil circuit and check valve, the sealing property and operating stability of the high-pressure oil pump test device of the present application are improved, and the performance test of high-pressure oil pump under the actual working condition of simulating high speed and high pressure can be realized.

Description

Technical Field

[0001] This invention relates to the field of testing, and more specifically to a testing device for a high-pressure oil pump. Background Technology

[0002] High-pressure oil pumps are widely used in various industrial equipment such as engines, jacks, and cranes, providing fuel pressure support. Their reliability and service life directly determine the operational stability of the entire equipment. In actual working conditions, high-pressure oil pumps often operate under high loads for extended periods: continuous operation, excessive flow rates, or excessively high pressures can all negatively impact their lifespan. High-load operation places greater stress on components such as the plunger rod and plunger spring seat, making them more prone to failure. Therefore, during the selection and design phase of high-pressure oil pumps, specialized testing equipment is typically used for simulation testing to verify whether their service life and stability meet design requirements. Existing high-pressure oil pump testing equipment needs to simulate actual high-speed, high-pressure conditions, placing high demands on the equipment's performance. Maintaining the sealing and operational stability of the equipment during testing remains a technical challenge that the industry needs to address. Summary of the Invention

[0003] To address the aforementioned problems in the prior art, this invention proposes a testing device for a high-pressure oil pump, comprising: The testing system includes a servo motor that drives a high-pressure oil pump to rotate at high speed. A sealing mechanism is provided between the servo motor and the high-pressure oil pump. The sealing mechanism includes a three-stage sealing mechanism that can gradually increase the pressure loss and perform three-stage sealing on the hydraulic oil. The oil circuit system includes multiple sets of oil delivery circuits, each connected to a first or second pump port of a high-pressure oil pump. Each set of oil delivery circuits is equipped with a check valve. By adjusting the check valve, the oil inlet and outlet states of the first and second pump ports of the high-pressure oil pump can be switched, thereby enabling performance testing under forward and reverse rotation conditions of the high-pressure oil pump.

[0004] By incorporating a three-stage sealing mechanism, the pressure loss can be progressively increased through these three stages, enhancing the sealing reliability of the testing device. The oil circuit system, with its multiple delivery oil lines and check valves, eliminates the need to disassemble and replace the external oil pipeline of the high-pressure oil pump. Simply adjusting the on / off state of the check valves allows for switching of operating conditions, avoiding problems such as pipeline seal failure and connection wear caused by repeated disassembly and assembly, effectively improving the stability of the testing process. Through the coordinated design of the sealing components, delivery oil lines, and check valves, this device improves the sealing performance and operational stability of the high-pressure oil pump testing equipment, enabling performance testing of the high-pressure oil pump under simulated high-speed, high-pressure actual operating conditions.

[0005] Furthermore, the sealing mechanism includes a splined shaft, a bearing, and a labyrinth sleeve. One end of the splined shaft is connected to a high-pressure oil pump, and the other end is connected to the servo motor. The bearing is sleeved on the splined shaft. The labyrinth sleeve is sleeved on the outside of the bearing. The labyrinth sleeve is connected to the high-pressure oil pump and forms a front cavity between the bearing and the high-pressure oil pump. The splined shaft, the bearing, and the labyrinth sleeve cooperate to form a first-stage seal for the hydraulic oil.

[0006] Furthermore, a retaining ring extending toward the spline shaft is provided on the side of the labyrinth sleeve near the high-pressure oil pump, and the retaining ring abuts against the bearing; a bearing end cap is provided on the side of the bearing away from the high-pressure oil pump, the bearing end cap is sleeved on the spline shaft, and the bearing end cap and the labyrinth sleeve are fixedly connected, and the bearing end cap and the retaining ring clamp and fix the bearing.

[0007] Furthermore, the bearing end cap is sleeved on the splined shaft, and the surface of the bearing end cap's sleeve hole is separated from the surface of the splined shaft, leaving a gap between them. An annular gap flow channel is formed between the bearing end cap and the splined shaft, and the width of the gap flow channel is 0.02mm~0.05mm. The gap flow channel forms a second-stage seal for the hydraulic oil.

[0008] Furthermore, the bearing end cover has an annular extension on the side near the servo motor towards the servo motor. The annular extension and the bearing end cover are coaxially arranged. The annular extension is sleeved on the spline shaft. The sleeve hole surface of the annular extension is separated from the surface of the spline shaft, and a gap is left between them. The gap width is 0.02mm~0.05mm.

[0009] Furthermore, an adapter shaft is installed at the end of the splined shaft away from the high-pressure oil pump. A gap is reserved between the adapter shaft and the bearing end cover to form a rear cavity. The adapter shaft has a square groove, and a square rod is provided at the end of the splined shaft. The square rod is inserted and accommodated in the square groove. When the adapter shaft rotates, it can drive the splined shaft to rotate synchronously. An oil seal is fitted on the adapter shaft. The outer ring of the oil seal is connected to the oil seal seat, and the lip of the inner ring is fitted to the adapter shaft. The adapter shaft and the oil seal cooperate to form a third-level seal for the hydraulic oil.

[0010] Furthermore, two sets of oil seals are provided, and the two sets of oil seals are sleeved side by side along the axial direction on the adapter shaft, separated by a retaining ring.

[0011] Furthermore, the sealing mechanism also includes an oil circuit board, which is sleeved on the bearing end cover. The oil circuit board has a pressure relief pipe, one end of which is connected to the rear cavity and the other end is connected to the outside of the testing device. A relief groove is opened at the position of the bearing end cover corresponding to the port of the pressure relief pipe, so that hydraulic oil can collect in the relief groove and be discharged from the pressure relief pipe.

[0012] Furthermore, the hydraulic system includes a fixed displacement pump and a pressure regulating mechanism. The fixed displacement pump delivers hydraulic oil to the high-pressure oil pump. After passing through the high-pressure oil pump, the hydraulic oil flows into the oil tank through the pressure regulating mechanism. The oil delivery circuit includes a first oil circuit and a second oil circuit. The inlets of both the first and second oil circuits are connected to a metering pump. The outlet of the first oil circuit is connected to the first pump port of the high-pressure oil pump, and the outlet of the second oil circuit is connected to the second pump port of the high-pressure oil pump. The oil conveying circuit also includes a third oil circuit and a fourth oil circuit. The oil outlets of the third oil circuit and the fourth oil circuit are both connected to the pressure regulating mechanism. The oil inlet of the third oil circuit is connected to the first pump port of the high-pressure oil pump, and the oil inlet of the fourth oil circuit is connected to the second pump port of the high-pressure oil pump. One-way valves are provided in the first oil circuit, the second oil circuit, the third oil circuit and the fourth oil circuit. By adjusting the one-way valves, the oil inlet and outlet states of the first pump port and the second pump port can be switched.

[0013] Furthermore, the testing device is equipped with multiple independent oil circuit systems and testing systems. Each set of oil circuit systems is individually connected to a set of testing systems, and the testing device can test multiple high-pressure oil pumps simultaneously. Attached Figure Description

[0014] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an improper limitation of the invention.

[0015] To more clearly illustrate the technical solutions in the embodiments of the present invention, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0016] Figure 1 This is a perspective view of a test apparatus for a high-pressure oil pump according to an embodiment of the present invention; Figure 2 This is a perspective view of a high-pressure oil pump testing device according to an embodiment of the present invention after the outer casing has been removed. Figure 3 This is a perspective view of a testing system according to an embodiment of the present invention; Figure 4 A cross-section of a test system according to an embodiment of the present invention. Figure 1 ; Figure 5 for Figure 4 A magnified view of a portion of the image; Figure 6 A cross-section of a test system according to an embodiment of the present invention. Figure 2 ; Figure 7 for Figure 6 A magnified view of a portion of the image; Figure 8 This is a perspective view of a bearing end cap according to an embodiment of the present invention; Figure 9 This is a schematic diagram of the piping connection of a testing device for a high-pressure oil pump according to an embodiment of the present invention. Figure 1 ; Figure 10 This is a schematic diagram of the piping connection of a testing device for a high-pressure oil pump according to an embodiment of the present invention. Figure 2 ; Figure 11 This is an actual sample of a testing device for a high-pressure oil pump according to an embodiment of the present invention. Figure 1 ; Figure 12 This is an actual sample of a testing device for a high-pressure oil pump according to an embodiment of the present invention. Figure 2 .

[0017] The components include: 1. Worktable; 2. Servo motor; 3. Clutch; 4. Torque sensor; 5. Bearing support. 6. Sealing mechanism; 601. Splined shaft; 602. Bearing; 603. Labyrinth sleeve; 6031. Retaining ring; 604. Adapter plate; 605. Front cavity; 606. Bearing end cover; 607. Gap flow channel; 608. Protrusion; 609. Extension; 610. Alternating groove; 611. Adapter shaft; 612. Square groove; 613. Oil seal seat; 614. Retaining ring; 615. Oil seal; 616. Oil manifold; 617. Pressure relief pipe; 7. High-pressure oil pump; 8. Purification system; 80. Baffle; 81. Clean oil tank; 82. Sludge oil tank; 83. Liquid level sensor; 84. Temperature sensor; 85. Circulation pump; 86. Cooler; 87. Circulation filter; 9. Oil circuit system; 91. Metering pump; 92. Filter; 93. Pressure regulating valve; 94. Oil circuit; 941. First oil circuit; 942. Second oil circuit; 943. Third oil circuit; 944. Fourth oil circuit; 95. Check valve; 96. Pressure sensor; 97. Pressure regulating mechanism; 971. Flow meter; 972. Pressure gauge; 973. Pressure measuring interface; 974. Proportional self-regulating valve; 975. Relief valve; 98. Return filter. Detailed Implementation

[0018] To make the above-mentioned objects, features, and advantages of the present invention more apparent and understandable, specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a thorough understanding of the present invention. However, the present invention can be practiced in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below.

[0019] See appendix Figure 1 , 2 As shown in Figures 11 and 12, the testing device for the high-pressure oil pump in this embodiment is used to simulate actual working conditions of high speed and high pressure to conduct performance tests on the high-pressure oil pump.

[0020] See appendix Figure 3-8 As shown, the testing device includes a hydraulic circuit system 9 and a testing system. The testing system includes a workbench 1, on which a servo motor 2 is mounted. The servo motor 2 is connected to a high-pressure oil pump 7 via a clutch 3. Two sets of clutches 3 are provided to improve testing safety. A torque sensor 4 is installed between the two sets of clutches 3. A bearing support 5 is installed at the right end of the clutch 3, and the bearing support 5 is rotated by the servo motor 2. A sealing mechanism 6 is provided between the bearing support 5 and the high-pressure oil pump to seal the front end of the high-pressure oil pump, preventing oil pressure from impacting the shaft system under high pressure and high speed conditions, which could lead to unstable oil pressure and hydraulic oil leakage. In this application, the end closer to the servo motor 2 is the left end, and the end closer to the high-pressure oil pump 7 is the right end.

[0021] The sealing mechanism 6 includes a bearing 602, which is sleeved on a splined shaft 601. One end of the splined shaft 601 is connected to the input shaft of the high-pressure oil pump 7, and the other end is connected to the bearing support 5. Driven by the servo motor 2, the splined shaft 601 drives the impeller inside the high-pressure oil pump 7 to rotate. There are two sets of bearings 602 arranged in parallel.

[0022] The sealing mechanism 6 also includes a labyrinth sleeve 603, which is fitted onto the outside of the two sets of bearings 602. The labyrinth sleeve 603 is connected to the high-pressure oil pump 7 via an adapter plate 604, and separates a front chamber 605 between the bearings 602 and the high-pressure oil pump 7. The pressure in the front chamber 605 is the test pressure, which is 50 bar. The two sets of bearings 602 are arranged on the left side of the high-pressure oil pump 7. The splined shaft 601, bearings 602, and labyrinth sleeve 603 work together to form the first-stage seal for the hydraulic oil, which increases pressure loss, reduces oil pressure, and prevents high-pressure oil from impacting and damaging the left-side shaft system.

[0023] A retaining ring 6031 protruding towards the spline shaft 601 is provided at the right end of the labyrinth sleeve 603. This retaining ring 6031 abuts against the bearing 602 seat, achieving axial positioning of the right side of the bearing 602. A bearing end cover 606 is provided on the left side of the bearing 602. The bearing end cover 606 is sleeved on the spline shaft 601, completing the position fixation of the left end of the bearing 602. Through the cooperation of the bearing end cover 606 and the retaining ring 6031, the axial positioning of the bearing 602 within the bearing 602 seat is achieved. When the spline shaft 601 rotates during operation, the inner ring of the bearing 602 rotates synchronously with the spline shaft, and the outer ring is locked in the inner cavity formed by the bearing end cover and the labyrinth sleeve. This positioning structure can stably withstand the radial load and axial impact transmitted by the spline shaft, structurally preventing axial movement and offset of the spline shaft during high-speed operation, and ensuring stable transmission accuracy.

[0024] The bearing end cap 606 has an annular structure with a connecting hole on its annular edge for fixed connection with the labyrinth sleeve 603. A protrusion 608 extending towards the bearing 602 is provided on the right side of the bearing end cap 606. During assembly, the protrusion 608 abuts against the bearing 602, achieving axial fixation of the bearing 602 and simplifying the assembly process. The protrusion 608 is preferably an annular structure, which further enhances the fixing effect on the bearing 602.

[0025] A bearing end cap 606 is fitted onto a splined shaft 601, with its bore surface separate from the surface of the splined shaft 601, leaving a gap between them. An annular gap channel 607 is formed between the bearing end cap and the splined shaft. The width of the gap channel 607 is 0.02mm to 0.05mm, preferably 0.03mm. The gap channel 607 forms a second-stage seal for the hydraulic oil. By increasing the pressure drop through the gap channel 607, the pressure in the rear chamber can be stabilized at approximately 5 bar. This design utilizes the gap channel 607 for throttling to achieve pressure reduction and stabilization. Compared to the traditional pressure reduction scheme of machining throttling holes on the end cap, this eliminates the additional drilling process and structurally avoids the problem of impurities in the oil clogging the throttling holes and causing pressure instability. Meanwhile, the annular gap flow channel 607 also provides a deformation allowance for thermal expansion and contraction of the spline shaft 601, avoiding dry friction and scratching between the shaft and the end cover under alternating high and low temperature conditions. This can effectively reduce the risk of abnormal wear of the transmission components, improve the reliability of the device operation, and extend the maintenance cycle and service life of the whole machine.

[0026] In some embodiments, an annular extension 609 is coaxially disposed on the left side of the bearing end cover 606 facing the servo motor direction. The annular extension 609 and the bearing end cover 606 are coaxially disposed, and the annular extension 609 is sleeved on the spline shaft 601. The surface of the sleeve hole of the annular extension 609 is separate from the surface of the spline shaft 601, with a gap between them. The gap width is 0.02mm~0.05mm, preferably 0.03mm. By providing the extension 609, the length of the gap flow channel is increased, which can extend the leakage flow path of hydraulic oil in the bearing 602 cavity, increase the leakage resistance, effectively reduce the probability of hydraulic oil leakage to the outside, and improve the stability of the lubrication state of the bearing 602. The bearing end cover 606, the extension 609, and the protrusion 608 are integrally formed, which can improve the pressure resistance of the end cover.

[0027] In some embodiments, a transition shaft 611 is provided at the left end of the spline shaft 601, a square groove 612 is provided at the right side of the transition shaft 611, a square rod is provided at the end of the spline shaft 601, and the direction rod is accommodated in the square groove 612. During the rotation of the transition shaft 611, the spline shaft 601 is driven to rotate.

[0028] The oil seal seat 613 is sleeved on the adapter shaft 611, and the oil seal seat 613 is detachably connected to the bearing support seat 5 through a heat insulation ring. A gap is reserved between the oil seal seat 613 and the adapter shaft 611 to form a receiving cavity; the oil seal 615 is installed in the receiving cavity and sleeved on the adapter shaft 611. The outer ring of the oil seal 615 is connected to the oil seal seat 613, and the inner ring lip is set to fit against the adapter shaft 611 to form a seal at the rear cavity. The adapter shaft 611 and the oil seal 615 cooperate to form a third-level seal for the hydraulic oil, preventing the hydraulic oil from leaking towards the bearing support seat 5.

[0029] Two sets of oil seals 615 are provided, arranged side-by-side axially on the adapter shaft 611, separated by a retaining ring 614. The main oil seal is located on the side of the retaining ring 614 closer to the bearing 602, primarily responsible for preventing hydraulic oil from flowing towards the bearing support 5. The compensating oil seal is located on the left side of the retaining ring 614, used to collect any small amount of hydraulic oil that leaks towards the bearing support 5 due to incomplete sealing by the main oil seal. The coordinated arrangement of the two sets of oil seals 615 improves the overall sealing effect.

[0030] Within the sealing mechanism 6, the first-stage seal initially reduces pressure, increasing pressure loss. The second-stage seal, located in the gap flow channel 607, further increases pressure loss, stabilizing the pressure in the rear chamber at approximately 5 bar. Finally, the third-stage seal enhances overall sealing performance, ensuring hydraulic oil does not leak from the bearing support. The synergistic effect of the first, second, and third-stage seals progressively increases pressure loss and improves sealing reliability. When a test pressure of 50 bar is applied to the front chamber 605, hydraulic oil does not leak from the bearing support 5, allowing for successful completion of the high-pressure oil pump performance test.

[0031] In some embodiments, the right side of the oil circuit board 616 is fitted onto the labyrinth sleeve 603 and fixedly connected to the labyrinth sleeve 603 by bolts, while the left side is fitted onto the bearing end cover 606. A pressure relief pipe 617 is provided on the oil circuit board 616. One end of this pipe connects to the rear cavity, and the other end connects to an external oil tank of the test system. When the pressure in the rear cavity exceeds a preset value, pressure relief can be achieved through the pressure relief pipe 617. The pressure relief pipe 617 can promptly discharge excess pressure generated inside the rear cavity due to oil agitation, temperature rise, etc., preventing high-pressure oil from breaking through the sealing surface of the oil seal 615 and causing leakage. Simultaneously, the flowing oil and gas can carry away the heat generated by the rotational friction of the bearing 602, reducing the operating temperature of the bearing 602 cavity, delaying the aging and failure of the rubber seals and the fatigue wear of the bearing 602, and extending the service life of the core transmission components.

[0032] A relief groove 610 is formed at the edge of the bearing end cover 606 corresponding to the port of the pressure relief pipe 617. This allows hydraulic oil to collect within the relief groove 610 and drain out through the pressure relief pipe 617. The depth of the relief groove 610 is controlled between 1.5mm and 2.5mm, and the groove width is 1mm to 2mm larger than the diameter of the port of the pressure relief pipe 617. This ensures sufficient space for the hydraulic oil to collect and flow without weakening the overall structural strength of the end cover due to excessive groove size. A rounded corner of R0.3mm to R0.5mm is machined at the corner of the groove to eliminate stress concentration points caused by the groove and reduce the risk of cracking and failure of the end cover due to long-term oil pressure impact.

[0033] The synergistic effect of bearing 602, clearance flow channel 607, and oil seal 615 forms a three-stage sealing structure, progressively increasing pressure loss and improving sealing reliability. In conjunction with pressure relief pipe 617, the pressure in the rear cavity is promptly discharged, and the small amount of hydraulic oil leaking into the sealing gaps of each stage is diverted back to the oil tank. This prevents excessive oil pressure from causing abnormal changes in the interference fit of the lip of oil seal 615, accelerated wear, or even flange failure. It can systematically block the path of lubricating oil leakage outward along the axis from a structural level, improving the overall stability and reliability of the equipment operation.

[0034] See appendix Figure 2 , 9As shown in Figure 10, the testing device also includes a purification system 8, which comprises a clean oil tank 81, a sludge oil tank 82, and an oil purification mechanism. The oil purification mechanism includes a circulation pump 85 and a circulation filter 87 connected to the circulation pump 85. The inlet of the circulation pump 85 is connected to the sludge oil tank 82, and the outlet of the circulation filter 87 is connected to the clean oil tank 81. The hydraulic oil in the sludge oil tank 82 flows into the clean oil tank 81 after being filtered by the circulation filter 87 under the action of the circulation pump 85, thus completing the purification process. A cooler 86 is installed between the circulation pump 85 and the filter 82 to simultaneously cool the hydraulic oil during the purification process.

[0035] The clean oil tank 81 and the dirty oil tank 82 share the same oil tank body, and a partition 80 is set between them. When the oil level in the clean oil tank 81 is higher than the partition 80, the hydraulic oil in the clean oil tank 81 will flow back to the dirty oil tank 82. By ensuring that the oil level in the dirty oil tank 82 is not higher than the height of the partition 80, the hydraulic oil in the dirty oil tank 82 is prevented from flowing back directly to the clean oil tank 81.

[0036] A level sensor 83 and a temperature sensor 84 are respectively installed in the clean oil tank 81 and the sludge oil tank 82 to detect the oil level and temperature in the two tanks. An external level gauge is also installed on the outside of the sludge oil tank 82 so that the operator can directly observe the level of the sludge oil tank 82. This ensures that the level of the sludge oil tank 82 is never higher than the height of the partition 80, thus preventing unfiltered hydraulic oil in the sludge oil tank 82 from overflowing directly into the clean oil tank 81.

[0037] In some embodiments, the hydraulic system 9 includes a fixed displacement pump 91, which, driven by a motor, delivers hydraulic oil from the clean oil tank 81 to a high-pressure oil pump. After passing through the high-pressure oil pump, the hydraulic oil then passes through a pressure regulating mechanism 97 and a return filter 98 before finally flowing back into the clean oil tank 81, completing the hydraulic oil circulation.

[0038] The oil circuit system 9 also includes a filter 92 located on the rear side of the fixed displacement pump 91 for filtering hydraulic oil and protecting the equipment on the oil circuit pipeline; it also includes a pressure regulating valve 93, one port of which is connected to the fixed displacement pump 91 through a pipeline and the other port is connected to the oil tank through a pipeline, and the pressure of the hydraulic oil output by the fixed displacement pump 91 can be adjusted by the pressure regulating valve 93.

[0039] In some embodiments, the oil circuit system 9 includes a delivery oil circuit 94, which includes a first oil circuit 941 and a second oil circuit 942. The inlets of the first oil circuit 941 and the second oil circuit 942 are both connected to a metering pump 91. The outlet of the first oil circuit 941 is connected to the first pump port of the high-pressure oil pump, and the outlet of the second oil circuit 942 is connected to the second pump port of the high-pressure oil pump.

[0040] The oil conveying circuit 94 also includes a third oil circuit 943 and a fourth oil circuit 944: the oil outlets of the third oil circuit 943 and the fourth oil circuit 944 are both connected to the pressure regulating mechanism 97, the oil inlet of the third oil circuit 943 is connected to the first pump port of the high-pressure oil pump, and the oil inlet of the fourth oil circuit 944 is connected to the second pump port of the high-pressure oil pump.

[0041] One-way valves 95 are installed on the first oil circuit 941, the second oil circuit 942, the third oil circuit 943, and the fourth oil circuit 944. By adjusting the on / off state of the one-way valves 95, the oil inlet and outlet states of the first and second pump ports can be switched, thereby realizing performance testing under the forward and reverse rotation conditions of the high-pressure oil pump. This solution does not require disassembly and replacement of the external oil pipeline of the high-pressure oil pump. The switching of operating conditions can be completed simply by adjusting the on / off state of the one-way valves 95. Compared with the traditional disassembly and reassembly testing method, the time for a single switching of operating conditions can be reduced by more than 75%. At the same time, it avoids problems such as pipeline sealing failure and wear of connection interfaces caused by repeated disassembly and assembly, effectively improving the stability of the testing process and the repeatability of results.

[0042] Pressure sensors 96 are installed on both the third oil circuit 943 and the fourth oil circuit 944 to detect the pressure values ​​of the high-pressure oil pump in real time during forward and reverse rotation. The collected pressure signals are transmitted to the industrial control processing unit, which can simultaneously record the dynamic pressure changes during the forward oil supply phase and the reverse oil return phase of the high-pressure oil pump, generating continuous pressure change curves. Based on the standardized collected pressure data, key performance parameters such as average pressure, pressure fluctuation rate, and maximum pressure deviation of the high-pressure oil pump under different operating conditions can be calculated, providing quantitative support for the performance calibration, qualification determination, and fault diagnosis of the high-pressure oil pump.

[0043] In some embodiments, the pressure regulating mechanism 97 includes a flow meter 971, a temperature sensor 84, a pressure gauge 972, a pressure measuring interface 973, and a proportional automatic valve 974 connected in sequence. The proportional automatic valve 974 regulates the oil pressure in the oil circuit system 9. Each detection component collects the flow, temperature, and pressure parameters of the oil circuit in real time and transmits the collected parameters synchronously to the oil circuit control system. The control system can dynamically adjust the opening of the proportional automatic valve 974 in a closed loop based on a preset oil pressure operating threshold to ensure that the oil pressure of the oil circuit system 9 remains stable within the set operating range. The pressure measuring interface 973 can be reserved for the access conditions of external high-precision standard pressure testing equipment, which facilitates the periodic accuracy calibration of the built-in pressure gauge 972, corrects the measurement deviation caused by long-term operation of the instrument, and improves the accuracy and reliability of oil pressure regulation.

[0044] The pressure regulating mechanism 97 also includes a relief valve 975, the inlet of which is connected to the flow meter 971, and the outlet of which is connected to the oil tank. When the oil pressure in the hydraulic system 9 is too high, the hydraulic oil will flow back to the oil tank through the relief valve 975, thereby improving the safety of the hydraulic system 9.

[0045] In some embodiments, the testing device is provided with multiple independent oil circuit systems 9 and testing systems. Each oil circuit system 9 is connected to a separate testing system, which can test multiple pumps under test at the same time. The testing processes of each group are independent of each other and there is no interference.

[0046] In some embodiments, only one set of purification system 8 needs to be set up, which is shared by multiple sets of oil circuit systems 9, thereby reducing the number of components in the test device and lowering the manufacturing and maintenance costs of the test device.

[0047] The testing process for the high-pressure oil pump includes the following steps: S1. Start the metering pump 91, open the check valves 94 on the first oil circuit 941 and the fourth oil circuit 944, and pump hydraulic oil into the pipeline of the test device to reach the set pressure. S2. Start the servo motor 2 to drive the high-pressure oil pump 7 to rotate at the preset speed and in the forward direction. The hydraulic oil flows out from the first oil passage 941, enters the first pump port of the high-pressure oil pump 7, is discharged from the second pump port of the high-pressure oil pump 7, flows out through the fourth oil passage 944, and then flows back to the oil tank through the pressure regulating mechanism 97 and the return filter 98, thus completing the test of the forward rotation of the high-pressure oil pump 7. S3. Close the check valves 94 on the first oil circuit 941 and the fourth oil circuit 944, open the check valves 94 on the second oil circuit 942 and the third oil circuit 943, start the servo motor 2 to drive the high-pressure oil pump 7 to rotate at the preset speed and in the opposite direction. The oil flows out from the second oil circuit 942, enters the second pump port of the high-pressure oil pump 7, and is discharged from the first pump port of the high-pressure oil pump 7. It then flows out through the third oil circuit 943, and then flows back to the oil tank through the pressure regulating mechanism 97 and the return filter 98, thus completing the test of the high-pressure oil pump 7 rotating in the opposite direction.

[0048] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0049] The above embodiments are only for illustrating the technical concept and features of the present invention. Their purpose is to enable those skilled in the art to understand the content of the present invention and implement it. They should not be used to limit the scope of protection of the present invention. All equivalent changes or modifications made in accordance with the spirit and essence of the present invention should be covered within the scope of protection of the present invention.

Claims

1. A testing device for a high-pressure oil pump, characterized in that, include: The testing system includes a servo motor (2), which can drive a high-pressure oil pump (7) to rotate at high speed. A sealing mechanism (6) is set between the servo motor (2) and the high-pressure oil pump (7). The sealing mechanism (6) includes a three-stage sealing mechanism, which can gradually increase the pressure loss and perform three-stage sealing on the hydraulic oil. The oil circuit system (9) includes multiple sets of oil delivery circuits (94). The oil delivery circuits (94) are connected to the first or second pump port of the high-pressure oil pump (7). Each of the multiple sets of oil delivery circuits (94) is equipped with a check valve (95). By adjusting the check valve (95), the oil inlet and outlet states of the first and second pump ports of the high-pressure oil pump (7) can be switched, thereby realizing the performance test of the high-pressure oil pump (7) under forward and reverse rotation conditions.

2. The testing apparatus for the high-pressure oil pump according to claim 1, characterized in that, The sealing mechanism (6) includes a splined shaft (601), a bearing (602), and a labyrinth sleeve (603). One end of the splined shaft (601) is connected to the high-pressure oil pump (7), and the other end is connected to the servo motor (2). The bearing (602) is sleeved on the splined shaft (601). The labyrinth sleeve (603) is sleeved on the outside of the bearing (602). The labyrinth sleeve (603) is connected to the high-pressure oil pump (7) and forms a front cavity (605) between the bearing (602) and the high-pressure oil pump (7). The splined shaft (601), the bearing (602), and the labyrinth sleeve (603) cooperate to form a first-stage seal for the hydraulic oil.

3. The testing apparatus for the high-pressure oil pump according to claim 2, characterized in that, The labyrinth sleeve (603) has a retaining ring (6031) extending toward the spline shaft (601) on the side near the high-pressure oil pump (7), and the retaining ring (6031) abuts against the bearing (602); the bearing (602) has a bearing end cap (606) on the side away from the high-pressure oil pump (7), the bearing end cap (606) is sleeved on the spline shaft (601), and the bearing end cap and the labyrinth sleeve (603) are fixedly connected, and the bearing end cap (606) and the retaining ring (6031) clamp and fix the bearing (602).

4. The testing apparatus for the high-pressure oil pump according to claim 3, characterized in that, The bearing end cap (606) is sleeved on the spline shaft (601). The surface of the sleeve hole of the bearing end cap (606) is separated from the surface of the spline shaft (601), and a gap is left between them. An annular gap flow channel (607) is formed between the bearing end cap (606) and the spline shaft (601). The width of the gap flow channel (607) is 0.02mm~0.05mm. The gap flow channel (607) forms a second-stage seal for the hydraulic oil.

5. The testing apparatus for the high-pressure oil pump according to claim 4, characterized in that, The bearing end cover (606) has an annular extension (609) on the side near the servo motor (2) towards the servo motor. The annular extension (609) and the bearing end cover (606) are coaxially arranged. The annular extension (609) is sleeved on the spline shaft (601). The sleeve hole surface of the annular extension (609) is separated from the surface of the spline shaft (601), and there is a gap between them with a gap width of 0.02mm~0.05mm.

6. The testing apparatus for the high-pressure oil pump according to claim 4, characterized in that, The spline shaft (601) is equipped with a transition shaft (611) at the end away from the high-pressure oil pump (7). A gap is reserved between the transition shaft (611) and the bearing end cover to form a rear cavity. The transition shaft (611) has a square groove (612). A square rod is provided at the end of the spline shaft (601). The square rod is inserted into the square groove (612). When the transition shaft (611) rotates, it can drive the spline shaft (601) to rotate synchronously. An oil seal (615) is fitted on the transition shaft (611). The outer ring of the oil seal (615) is connected to the oil seal seat (613). The lip of the inner ring is fitted to the transition shaft (611). The transition shaft (611) and the oil seal (615) cooperate to form a third-level seal for the hydraulic oil.

7. The testing apparatus for the high-pressure oil pump according to claim 6, characterized in that, Two sets of oil seals (615) are provided. The two sets of oil seals (615) are sleeved side by side along the axial direction on the adapter shaft (611) and separated by a retaining ring (614).

8. The testing apparatus for a high-pressure oil pump according to claim 6, characterized in that, The sealing mechanism (6) also includes an oil circuit board (616), which is sleeved on the bearing end cover (606). A pressure relief pipe (617) is provided on the oil circuit board (616). One end of the pressure relief pipe (617) is connected to the rear cavity, and the other end is connected to the outside of the test device. A relief groove (610) is provided on the edge of the bearing end cover (606) at the position corresponding to the port of the pressure relief pipe (617). Hydraulic oil can be collected in the relief groove (610) and discharged from the pressure relief pipe (617).

9. The testing apparatus for a high-pressure oil pump according to claim 1, characterized in that, The oil circuit system (9) includes a metering pump (91) and a pressure regulating mechanism (97). The metering pump (91) delivers hydraulic oil to the high-pressure oil pump (7). After passing through the high-pressure oil pump (7), the hydraulic oil flows into the oil tank through the pressure regulating mechanism (97). The oil conveying circuit (94) includes a first oil circuit (941) and a second oil circuit (942). The oil inlets of the first oil circuit (941) and the second oil circuit (942) are both connected to a metering pump (91). The liquid outlet of the first oil circuit (941) is connected to the first pump port of the high-pressure oil pump (7), and the liquid outlet of the second oil circuit (942) is connected to the second pump port of the high-pressure oil pump (7). The oil conveying circuit (94) also includes a third oil circuit (943) and a fourth oil circuit (944). The oil outlets of the third oil circuit (943) and the fourth oil circuit (944) are connected to the pressure regulating mechanism (97). The oil inlet of the third oil circuit (943) is connected to the first pump port of the high-pressure oil pump (7), and the oil inlet of the fourth oil circuit (944) is connected to the second pump port of the high-pressure oil pump (7). One-way valves (95) are provided on the first oil passage (941), the second oil passage (942), the third oil passage (943) and the fourth oil passage (944). By adjusting the one-way valves (95), the oil inlet and outlet states of the first pump port and the second pump port can be switched.

10. The testing apparatus for a high-pressure oil pump according to claim 1, characterized in that, The testing device is equipped with multiple independent oil circuit systems (9) and testing systems. Each set of oil circuit systems (9) is connected to a separate set of testing systems. The testing device can test multiple high-pressure oil pumps (7) at the same time.

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