Microcomputer-controlled hydraulic pipeline component bending fatigue test bench

Abstract

The present invention discloses a microcomputer-controlled hydraulic pipeline component bending fatigue test bench, which includes a test bench and a control console. An installation base plate is provided inside the test bench. A rotating integrated head seat is provided on the installation base plate. A plurality of rotating wheels are provided inside the rotating integrated head seat, and the rotating wheels are driven by a driving device. An eccentric mechanism is provided outside the rotating integrated head seat. A tailstock guide rail is provided on the installation base plate. A tailstock is provided on the tailstock guide rail. A direction adjustment mechanism is provided on the tailstock. An oil inlet block is provided on the direction adjustment mechanism, and the oil inlet block is connected to an oil inlet mechanism. By providing a mechanism that can drive a plurality of eccentric mechanisms to rotate, the time required for the entire testing process is reduced. And through the use of the eccentric mechanism and the oil supply structure that can adjust the X, Y, and Z axes directions of the oil supply end, while fixing the bent pipe fittings, different pressures of liquid can be introduced into the pipe fittings to achieve comprehensive detection of them.

Description

Technical Field

[0001] The invention relates to the technical field of pressure testing, in particular to a test bench for testing bending fatigue of hydraulic pipeline components. Background Art

[0002] The bending fatigue life of hydraulic conduits and connectors directly affects the safety of the entire aircraft. Fatigue damage is known as the "killer" of aircraft safety and is a very concerning issue in the aviation field. The current hydraulic pipeline bending fatigue test bench equipment is mainly a test equipment for the rotational bending fatigue strength test of rigid conduit components such as aviation hydraulic conduit components. With the development of the market, in order to more accurately test the bending fatigue life of aircraft hydraulic conduits and connectors, improve the detection efficiency and the number of test pieces during the hydraulic pipeline bending fatigue test bench test, and control the function and test efficiency, there are higher requirements to meet the needs of market development. Summary of the invention

[0003] The purpose of the present invention is to provide a microcomputer-controlled hydraulic pipeline bending fatigue test bench to solve the pressure and fatigue performance test of the curved pipeline.

[0004] To achieve the above-mentioned purpose, the present invention provides the following technical solutions: a microcomputer-controlled hydraulic pipeline bending fatigue test bench, comprising a test bench and a control console, the control console being connected to the test bench by electrical signals, a mounting base plate being provided inside the test bench, a rotating integrated head seat being provided on the mounting base plate, a plurality of rotating wheels being provided inside the rotating integrated head seat, and the rotating wheels being driven by a driving device, an eccentric mechanism being provided outside the rotating integrated head seat, and the eccentric mechanism being installed at both ends of the rotating wheels;

[0005] The mounting base plate is provided with a tailstock guide rail, a tailstock is arranged on the tailstock guide rail, a direction adjustment mechanism is arranged on the tailstock, an oil inlet block is arranged on the direction adjustment mechanism, and the oil inlet block is connected to the oil inlet mechanism.

[0006] Preferably, the driving device is a motor, and the motor and the rotating wheel are driven by a transmission belt.

[0007] Preferably, the eccentric mechanism is provided with a turntable and an eccentric member, and the eccentric member is arranged on the turntable; the turntable is provided with an eccentric adjustment block, and the eccentric adjustment block is provided with a first screw, and the position of the eccentric member is adjusted by the first screw on the eccentric adjustment block, and the eccentric member is provided with a low-friction automatic centering bearing.

[0008] Preferably, the direction adjusting mechanism is provided with an X-axis direction adjusting block, an X-axis direction moving block and a trapezoidal block which cooperate with each other. A second screw is provided on the X-axis direction adjusting block, and the X-axis direction adjusting block is connected to the X-axis direction moving block through the second screw. A third screw capable of adjusting the Y-axis direction is provided on the X-axis direction moving block, and the third screw is connected to the trapezoidal block, and the trapezoidal block cooperates with the oil inlet block.

[0009] Preferably, the tailstock is provided with a tailstock locking structure.

[0010] Preferably, there are multiple rotating wheels; the eccentric mechanism is installed at both ends of the rotating wheel shaft.

[0011] Preferably, the oil inlet mechanism is provided with a low-pressure gas-driven liquid pump and a high-pressure gas-driven liquid pump. The low-pressure gas-driven liquid pump is connected to a medium oil tank and a gas source. The low-pressure gas-driven liquid pump is connected to the high-pressure gas-driven liquid pump, and the high-pressure gas-driven liquid pump is connected to the oil inlet block;

[0012] A check valve is connected in parallel to the low-pressure gas-driven liquid pump. The high-pressure gas-driven liquid pump is connected to the medium oil tank through the check valve, and the high-pressure gas-driven liquid pump is connected to the gas source.

[0013] Preferably, a medium oil suction filter and an oil suction ball valve are provided between the low-pressure gas-driven liquid pump and the check valve and the medium oil tank. The low-pressure gas-driven liquid pump is connected to the gas source through a low-pressure gas-driven liquid pump solenoid valve, a proportional regulating valve and a gas filter in sequence. The high-pressure gas-driven liquid pump is connected to the gas source through a high-pressure gas-driven liquid pump solenoid valve, a proportional regulating valve and a gas filter in sequence.

[0014] Compared with the prior art, the beneficial effects of the present invention are as follows: Through the technical solution proposed by the present invention, the problems existing in the pressure and fatigue performance tests of bent pipelines can be solved. By setting a structure capable of driving multiple eccentric mechanisms to rotate, multiple specimens to be tested can be tested simultaneously, reducing the time required for the entire test process. And through the use of the eccentric mechanism and the oil supply end capable of adjusting the X, Y, and Z axes directions, while fixing the bent pipe fittings, different pressures of liquid can be introduced into the pipe fittings, so as to provide pressure inside the pipe fittings during the rotation of the specimens to be tested, and comprehensive detection of them can be realized.

[0015] By setting a multi-stage gas-driven liquid pressurization method, the test pressure range is wider, the pressure dead zone is smaller, and the applicable range of pressure is guaranteed, so that the entire test process is more accurate. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 It is a schematic structural diagram of a microcomputer-controlled hydraulic pipeline component bending fatigue test bench of the present invention.

[0017] Figure 2This is a schematic diagram of the test bench for the bending fatigue test of microcomputer-controlled hydraulic pipeline components of the present invention.

[0018] Figure 3 This is a schematic diagram of the interior of the test bench for the bending fatigue test of microcomputer-controlled hydraulic pipeline components of the present invention.

[0019] Figure 4 This is a schematic diagram of the interior of the test bench for the bending fatigue test of microcomputer-controlled hydraulic pipeline components of the present invention.

[0020] Figure 5 This is a schematic diagram of the drive device of the test bench for the bending fatigue test of microcomputer-controlled hydraulic pipeline components of the present invention.

[0021] Figure 6 This is a schematic diagram of the eccentric mechanism of the test bench for the bending fatigue test of microcomputer-controlled hydraulic pipeline components of the present invention.

[0022] Figure 7 This is a schematic diagram of the eccentric mechanism of the test bench for the bending fatigue test of microcomputer-controlled hydraulic pipeline components of the present invention.

[0023] Figure 8 This is a schematic diagram of the direction adjustment mechanism of the test bench for the bending fatigue test of microcomputer-controlled hydraulic pipeline components of the present invention.

[0024] Figure 9 This is a schematic diagram of the direction adjustment mechanism of the test bench for the bending fatigue test of microcomputer-controlled hydraulic pipeline components of the present invention.

[0025] Figure 10 This is a schematic diagram of the oil inlet mechanism of the test bench for the bending fatigue test of microcomputer-controlled hydraulic pipeline components of the present invention.

[0026] 1. Test bench; 2. Control console; 3. Installation base plate; 4. Rotary integrated head seat; 5. Rotating wheel; 6. Eccentric mechanism; 7. Tailstock guide rail; 8. Tailstock; 9. Oil inlet block; 10. Motor; 11. Turntable; 12. Eccentric part; 13. Eccentric adjustment block; 14. First screw; 15. Low-friction automatic centering bearing; 16. X-axis direction adjustment block; 17. X-axis direction moving block; 18. Trapezoidal block; 19. Second screw; 20. Third screw; 21. Low-pressure gas-driven liquid pump; 22. High-pressure gas-driven liquid pump; 23. Medium oil tank; 24. Check valve; 25. Medium oil suction filter; 26. Oil suction ball valve; 27. Low-pressure gas-driven liquid pump solenoid valve; 28. Proportional regulating valve; 29. Air filter; 30. High-pressure gas-driven liquid pump solenoid valve. Detailed implementation method

[0027] The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts shall fall within the protection scope of the present invention.

[0028] Please refer to Figures 1-10 , the present invention provides a technical solution: a microcomputer-controlled hydraulic pipeline component bending fatigue test bench, including a test bench 1 and a control console 2. The control console 2 is electrically connected to the test bench 1. An installation base plate 3 is provided in the test bench 1. A rotary integrated head seat 4 is provided on the installation base plate 3. A plurality of rotating wheels 5 are provided in the rotary integrated head seat 4 to achieve the effect of driving a plurality of test pieces, and the rotating wheels 5 are driven by a driving device. An eccentric mechanism 6 is provided outside the rotary integrated head seat 4, and the eccentric mechanism 6 is installed at both ends of the rotating wheel 5 axis to test the test pieces before and after the rotary integrated head seat 4 on the test bench. When performing a fatigue test on the test piece, it is necessary to adjust the eccentric position of the eccentric mechanism 6 according to its situation.

[0029] In order to conveniently adjust the position of the tailstock 8 according to the specific length of the test piece, a tailstock guide rail 7 is provided on the installation base plate 3. A tailstock 8 is provided on the tailstock guide rail 7. A direction adjustment mechanism is provided on the tailstock 8. An oil inlet block 9 is provided on the direction adjustment mechanism to enable the position of the oil inlet block 9 to be adjusted and achieve precise centering with the eccentric member 12. The oil inlet block 9 is connected to the oil inlet mechanism.

[0030] The driving device is provided with a motor 10. The motor 10 is electrically connected to the control console 2, and the motor 10 and the rotating wheel 5 are driven by a transmission belt to drive all the rotating wheels 5 to rotate.

[0031] The eccentric mechanism 6 is provided with a turntable 11 and an eccentric member 12. An eccentric adjustment block 13 is provided on the turntable. A first screw 14 is provided in the eccentric adjustment block 13. The eccentric member 12 is screwed to the first screw 14, and the eccentric member 12 slides in the groove provided on the turntable 11 to achieve a directional effect. The eccentric member 12 is provided with a low-friction automatic centering bearing 15. One end of the test pipeline is installed in the low-friction automatic centering bearing 15, and the other end is installed with the oil inlet block 9 to achieve a positioning effect. Subsequently, the first screw 14 is rotated to adjust the eccentric position of the eccentric member 12 and the turntable 11, and then a bending stress can be applied to the test piece.

[0032] In order to adjust the position of the oil inlet block 9 in the Z-axis direction and simultaneously adjust the positions in the X and Y axes, the direction adjustment mechanism is provided with an X-axis direction adjustment block 16, an X-axis direction moving block 17, and a trapezoidal block 18 that cooperate with each other. The X-axis direction adjustment block 16 is provided with a second screw 19, and the X-axis direction moving block 17 is screwed to the second screw 19. The X-axis direction moving block 17 slides on the X-axis direction adjustment block 16 to achieve a directional effect. The X-axis direction moving block 17 is provided with a third screw 20 capable of adjusting the Y-axis direction, and the trapezoidal block 18 passes through the third screw 20 and is screwed to the third screw 20. The inclined upper surface of the trapezoidal block 18 slides on the inclined lower surface of the oil inlet block 9 to achieve the height adjustment of the oil inlet block 9 when the trapezoidal block 18 is displaced. In this way, rotating the second screw 19 and the third screw 20 can adjust the oil inlet block 9 in the X and Y axes, so as to ensure that the oil inlet block 9 can be aligned with the eccentric part 12 under the condition of zero eccentricity between the eccentric part 12 and the turntable 11, thereby achieving precise centering.

[0033] The tailstock 8 is provided with a tailstock locking structure, and the locking structure is a fastening screw screwed to the tailstock 8.

[0034] The test specimens and the requirements for the test are different, so the pressures borne by the test specimens during the test are different. Therefore, the range of test pressures is relatively large, and it is not conducive to ensuring the control accuracy of the test pressure in all pressure segments within the test pressure range during use. Therefore, this device adopts a multi-stage gas-driven liquid boosting method. The oil inlet mechanism is provided with a low-pressure gas-driven liquid pump 21 and a high-pressure gas-driven liquid pump 22. When the test pressure is lower than 8 MPa, the low-pressure gas-driven liquid pump 21 provides the pressure. Since the pressure boost ratio of the low-pressure gas-driven liquid pump 21 is lower than that of the high-pressure gas-driven liquid pump 22, the pressure control accuracy within the test pressure range below 8 MPa can be ensured; when the test pressure is higher than 8 MPa, the high-pressure gas-driven liquid pump 22 provides the pressure. The low-pressure gas-driven liquid pump 21 is connected to a medium oil tank 23 and a gas source. The low-pressure gas-driven liquid pump 21 is connected to the high-pressure gas-driven liquid pump 22, and the high-pressure gas-driven liquid pump 22 is connected to the oil inlet block 9, thereby achieving the oil supply effect.

[0035] The low-pressure gas-driven liquid pump 21 is connected in parallel with a one-way valve 24. The high-pressure gas-driven liquid pump 22 is connected to the medium oil tank 23 through the one-way valve 24 to achieve the separate oil supply effect of the high-pressure gas-driven liquid pump 22 when the test pressure is greater than 8 MPa. The high-pressure gas-driven liquid pump 22 is connected to the gas source.

[0036] A medium suction filter 25 and a suction oil ball valve 26 are provided between the low-pressure gas-driven liquid pump 21, the one-way valve 24 and the medium oil tank 23 to protect the cleanliness of the oil products entering the liquid pump and facilitate the maintenance and servicing of the system. The low-pressure gas-driven liquid pump 21 is connected to the gas source through a low-pressure gas-driven liquid pump solenoid valve 27, a proportional regulating valve 28 and a gas filter 29 in sequence, and the high-pressure gas-driven liquid pump 22 is connected to the gas source through a high-pressure gas-driven liquid pump solenoid valve 30, a proportional regulating valve 28 and a gas filter 29 in sequence to supply clean air to the low-pressure gas-driven liquid pump 21 and the high-pressure gas-driven liquid pump 22. Electric components are electrically connected to the control console 2, and an appropriate pressure ratio is selected. The test pressure range converted and output by the low-pressure gas-driven liquid pump 21 and the high-pressure gas-driven liquid pump 22 is wider, and the selectable test pressure dead zone is smaller, ensuring the test pressure adjustment range.

[0037] Working principle: Before using the equipment, adjust the position of the eccentric member 12 relative to the turntable 11 so that the eccentric member 12 and the turntable 11 are at zero eccentricity. Adjust the second screw 19 and the third screw 20 according to the actual condition of the equipment to adjust the oil inlet block 9 on the X and Y axes to achieve precise alignment with the eccentric member 12. After adjustment, the oil inlet block 9 does not need to be adjusted again (when replacing relevant parts, the oil inlet block 9 needs to be readjusted), and fix the position of the oil inlet block 9; before testing the test piece, first connect one end of the test piece to the oil inlet block 9, and then according to the strain gauge method, install the other end of the test piece on the low-friction automatic centering bearing 15 on the eccentric member 12, lock the tailstock 8, and adjust the first screw 14 to generate bending stress on the test piece, observe the strain measurement result of the test piece, and thus adjust the eccentricity of the eccentric member 12 relative to the turntable 11 to meet the test requirements. Then input the test required pressure to the test piece, and then make the turntable rotate at a constant speed at a certain frequency within the range of 1500 - 3600 r / min according to the test requirements.

[0038] During the test, the oil supply pressure can be selected according to the specific situation of the test tube. When the oil supply pressure is less than 8 MPa, select the low-pressure gas-driven liquid pump 21 to work, close the high-pressure gas-driven liquid pump 22 and the high-pressure gas-driven liquid pump solenoid valve 30, open the low-pressure gas-driven liquid pump 21 and the low-pressure gas-driven liquid pump solenoid valve 27, output air pressure through the proportional regulating valve 28 to drive the low-pressure gas-driven liquid pump 21 to work. The low-pressure gas-driven liquid pump 21 sucks the test medium from the medium oil tank 23, the medium suction filter 25 and the suction oil ball valve 26, converts it into the test pressure, and then passes it through the pump head of the high-pressure gas-driven liquid pump 22 into the oil inlet block 9.

[0039] When the oil supply pressure is greater than 8 MPa, the high-pressure gas-driven liquid pump 22 operates, the low-pressure gas-driven liquid pump 21 and the solenoid valve 27 of the low-pressure gas-driven liquid pump are closed, the high-pressure gas-driven liquid pump 22 and the solenoid valve 30 of the high-pressure gas-driven liquid pump are opened, and the air pressure is output through the proportional regulating valve 28 to drive the high-pressure gas-driven liquid pump 22 to operate. The high-pressure gas-driven liquid pump 22 sucks the test medium from the medium oil tank 23, the medium oil suction filter 25, the oil suction ball valve 26 and the check valve 24, converts it into the test pressure and directly supplies it to the oil inlet block 9.

[0040] Although the embodiments of the present invention have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions and variations can be made to these embodiments without departing from the principle and spirit of the present invention. The scope of the present invention is defined by the appended claims and their equivalents.

Claims

1. A microcomputer-controlled hydraulic pipeline component bending fatigue test bench, comprising a test bench (1) and a control console (2), wherein the control console (2) is electrically connected to the test bench (1), and is characterized in that: The test bench (1) is provided with a mounting base plate (3). A rotary integrated head seat (4) is arranged on the mounting base plate (3). A rotating wheel (5) is arranged inside the rotary integrated head seat (4), and the rotating wheel (5) is driven by a driving device. An eccentric mechanism (6) is arranged outside the rotary integrated head seat (4), and the eccentric mechanism (6) is installed on the shaft of the rotating wheel (5). The mounting base plate (3) is provided with a tailstock guide rail (7). A tailstock (8) is arranged on the tailstock guide rail (7). A direction adjusting mechanism is arranged on the tailstock (8). An oil inlet block (9) is arranged on the direction adjusting mechanism, and the oil inlet block (9) is connected to an oil inlet mechanism. The direction adjusting mechanism is provided with an X-axis direction adjusting block (16), an X-axis direction moving block (17) and a trapezoidal block (18) which cooperate with each other. A second screw (19) is arranged on the X-axis direction adjusting block (16). The X-axis direction adjusting block (16) is connected to the X-axis direction moving block (17) through the second screw (19). A third screw (20) capable of adjusting the Y-axis direction is arranged on the X-axis direction moving block (17), and the third screw (20) is connected to the trapezoidal block (18). The trapezoidal block (18) cooperates with the oil inlet block (9). The oil inlet mechanism is provided with a low-pressure gas-driven liquid pump (21) and a high-pressure gas-driven liquid pump (22). The low-pressure gas-driven liquid pump (21) is connected to a medium oil tank (23) and a gas source. The low-pressure gas-driven liquid pump (21) is connected to the high-pressure gas-driven liquid pump (22). The high-pressure gas-driven liquid pump (22) is connected to the oil inlet block (9). A one-way valve (24) is connected in parallel with the low-pressure gas-driven liquid pump (21). The high-pressure gas-driven liquid pump (22) is connected to the medium oil tank (23) through the one-way valve (24). The high-pressure gas-driven liquid pump (22) is connected to the gas source.

2. The microcomputer-controlled hydraulic pipeline component bending fatigue test bench according to claim 1, characterized in that The driving device is a motor (10), and the motor (10) is in transmission connection with the rotating wheel (5) through a transmission belt.

3. The microcomputer-controlled hydraulic pipeline component bending fatigue test bench according to claim 1, characterized in that, The eccentric mechanism (6) is provided with a turntable (11) and an eccentric member (12). The eccentric member (12) is arranged on the turntable (11). An eccentric adjusting block (13) is arranged on the turntable (11). A first screw (14) is arranged on the eccentric adjusting block (13). The position of the eccentric member (12) is adjusted through the first screw (14) on the eccentric adjusting block (13). A low-friction automatic centering bearing (15) is arranged on the eccentric member (12).

4. The microcomputer-controlled hydraulic pipeline component bending fatigue test bench according to claim 1, wherein, The tailstock (8) is provided with a tailstock locking structure.

5. The microcomputer-controlled hydraulic pipeline component bending fatigue test bench according to claim 1, characterized in that, There are multiple rotating wheels (5); the eccentric mechanism (6) is installed at both ends of the shaft of the rotating wheel (5).

6. The microcomputer-controlled hydraulic pipeline component bending fatigue test bench according to claim 1, characterized in that, A medium oil suction filter (25) and an oil suction ball valve (26) are arranged between the low-pressure gas-driven liquid pump (21) and the one-way valve (24) and the medium oil tank (23). The low-pressure gas-driven liquid pump (21) is connected to the gas source through a low-pressure gas-driven liquid pump solenoid valve (27), a proportional regulating valve (28) and a gas filter (29) in sequence. The high-pressure gas-driven liquid pump (22) is connected to the gas source through a high-pressure gas-driven liquid pump solenoid valve (30), a proportional regulating valve (28) and a gas filter (29) in sequence.

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