Hydraulic hose impact resistance test device based on rotary valve reversing and temperature control

Abstract

The utility model relates to the technical field of durability test, and discloses a hydraulic hose impact resistance test device based on rotary valve reversing and temperature control, which comprises a hydraulic pump and an energy accumulator, a stop valve is arranged at the inlet end of the energy accumulator, and the stop valve is opened or closed according to the working condition of a system. The hydraulic pump and the energy accumulator jointly provide flow for the rotary valve, the rotary valve is controlled by the servo motor, the servo motor receives signals of the pressure sensor through the computer so as to control the rotating speed and the rotating direction of the servo motor, the pressure sensor is arranged at the inlet end of a tested piece, and the inlet end of the tested piece is connected with a high-pressure cavity of the pressure cylinder. The outlet end is connected with the variable damper and the radiator. A slide valve type reversing valve is replaced by the rotary valve type reversing valve, high-pressure oil with the pressure changing in a pulse mode is continuously provided for the pressure cylinder, friction and abrasion are reduced, the reliability and the response speed of a system are improved, and the period of a pressure pulse test is shortened.

Description

Technical Field

[0001] The utility model relates to hydraulic test equipment, in particular to a hydraulic hose impact resistance test device based on rotary valve commutation and temperature control. Background Technique

[0002] Hydraulic hoses are widely used in aircraft hydraulic systems and often fail or are damaged due to reasons such as hydraulic pulses or overflows of relief valves causing heat generation. In severe cases, it may cause aircraft flight accidents. Therefore, it is necessary to conduct simulation tests on hydraulic hoses to simulate hydraulic pulses and high temperatures under actual working conditions, which is of great significance for ensuring the safe operation of aircraft hydraulic systems.

[0003] At present, most of the commutation controls for hydraulic hose pulse tests use spool-type servo valves. This commutation valve has high manufacturing and maintenance costs and is easily affected by pollution. As the working time increases, the spool often undergoes mechanical wear, resulting in increased leakage, thereby affecting the performance and efficiency of the valve, making the pulse generating device unable to generate the required pulse waveform. At the same time, due to reasons such as high-frequency hydraulic pulses or overflows of relief valves causing heat generation, currently, the hydraulic hose pulse system generally has high costs and low system working efficiency, which is not conducive to popularization. Content of the Utility Model

[0004] The purpose of the utility model is to provide a hydraulic hose impact resistance test device based on rotary valve commutation and temperature control.

[0005] The technical solution adopted by the utility model to solve its technical problems is:

[0006] A hydraulic hose impact resistance test device based on rotary valve commutation and temperature control includes a hydraulic pulse loading system, a temperature control system, and a servo control system; the hydraulic pulse loading system includes an oil source, a stop valve I, an accumulator, a rotary valve, a servo motor, a variable damping orifice I, a check valve II, and a booster cylinder; the oil source includes a main fuel tank, a hydraulic pump I, a check valve I, a relief valve I, and a directional control valve I, II; the temperature control system includes a variable damping orifice II, a radiator II, and a secondary fuel tank, as well as a stop valve II, a radiator I, and a relief valve II in the hydraulic system return oil circuit; the servo control system includes a servo motor, a controller, a temperature sensor, and a pressure sensor, and the servo motor is connected to the rotary valve.

[0007] The main fuel tank is connected to the inlet of the hydraulic pump I, the T ports of the directional control valves I, II, the stop valve II, the radiator I, and the outlet of the relief valve II;

[0008] The outlet of the hydraulic pump I is connected to the inlet of the check valve I;

[0009] The oil outlet of the one-way valve Ⅰ is respectively connected to the P port of the rotary valve, the inlet oil ports of the stop valve Ⅰ, the relief valve Ⅰ, and the P port of the reversing valve Ⅱ;

[0010] The oil outlet of the relief valve Ⅰ is connected to the P port of the reversing valve Ⅰ;

[0011] The T port of the rotary valve is connected to the inlet oil port of the one-way valve Ⅱ; the oil outlet of the one-way valve Ⅱ is respectively connected to the A port of the reversing valve Ⅰ, the stop valve Ⅱ, the inlet oil port of the radiator Ⅰ, and the inlet oil port of the relief valve Ⅱ;

[0012] The A port of the rotary valve is respectively connected to the variable damping port Ⅰ and the inlet oil port of the one-way valve Ⅲ;

[0013] The B port of the rotary valve is connected to the middle cavity of the booster cylinder;

[0014] The low-pressure cavity of the booster cylinder is respectively connected to the oil outlets of the one-way valve Ⅲ and the variable damping port;

[0015] The high-pressure cavity of the booster cylinder is respectively connected to the inlet oil port of the hydraulic hose and the oil outlet of the one-way valve Ⅳ;

[0016] The inlet oil port of the one-way valve Ⅳ is respectively connected to the oil outlet of the hydraulic pump Ⅱ and the inlet oil port of the relief valve Ⅲ;

[0017] The inlet oil port of the hydraulic pump Ⅱ and the oil outlet of the relief valve Ⅲ are both connected to the auxiliary oil tank;

[0018] The inlet oil port of the variable damping port Ⅱ is connected to the oil outlet of the hydraulic hose;

[0019] The oil outlet of the variable damping port is connected to the radiator Ⅱ;

[0020] The oil outlet of the radiator Ⅱ is connected to the auxiliary oil tank; the signal input end of the servo motor is connected to the signal output end of the controller.

[0021] The advantages of the present utility model are as follows:

[0022] Compared with the prior art, this test device replaces the spool-type reversing valve with a rotary valve, reducing friction and wear, improving the response speed of oil fluid commutation and the system sealing performance. At the same time, the rotary valve is controlled by a servo motor, the signal input end of the servo motor is connected to the signal output end of the controller, and the pressure sensor collects the pressure signal and transmits it to the controller, realizing automatic control with higher control precision; the variable damping port Ⅰ provides back pressure for the booster cylinder to prevent oil fluid from flowing back; in addition, cooling devices are provided in the main oil circuit, return oil circuit, and the outlet end of the test piece in the hydraulic pulse test system, and the temperature is maintained within a certain range according to the operating conditions required by the system, which ensures the system efficiency, prevents the temperature from being too high, extends the service life of the hydraulic oil fluid, and reduces mechanical wear. Description of the Drawings

[0023] Figure 1 It is a schematic structural diagram of a hydraulic hose impact resistance test device based on rotary valve commutation and temperature control proposed by the present utility model.

[0024] The descriptions of the main component symbols in the figure are as follows:

[0025] 1 Hydraulic pump Ⅰ 2 Relief valve Ⅱ 3 Radiator Ⅰ 4 Stop valve Ⅱ

[0026] 5 Directional control valve Ⅰ 6 Main oil tank 7 Directional control valve Ⅱ 8 Relief valve Ⅰ

[0027] 9 Check valve Ⅱ 10 Rotary valve 11 Servo motor 12 Variable damping orifice Ⅰ

[0028] 13 Check valve Ⅲ 14 Boost cylinder 15 Temperature sensor Ⅰ 16 Pressure sensor

[0029] 17 Controller 18 Temperature sensor Ⅱ 19 Check valve Ⅳ 20 Specimen to be tested

[0030] 21 Variable damping orifice Ⅱ 22 Radiator Ⅱ 23 Accumulator 24 Stop valve Ⅰ

[0031] 25 Check valve Ⅰ 26 Relief valve Ⅲ 27 Hydraulic pump Ⅱ 28 Auxiliary oil tank Specific embodiments

[0032] To make the objectives, technical solutions, and advantages of the embodiments of the present utility model clearer, the technical solutions in the embodiments of the present utility model will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present utility model. Obviously, the described embodiments are some, but not all, of the embodiments of the present utility model. Usually, the components of the embodiments of the present utility model described and illustrated herein can be arranged and designed in various different configurations. Therefore, the following detailed description of the embodiments of the present utility model provided in the drawings is not intended to limit the scope of the present utility model to be protected, but merely represents selected embodiments of the present utility model. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present utility model without making creative efforts fall within the protection scope of the present utility model.

[0033] As Figure 1 shown, the test device proposed by the present utility model includes a hydraulic pulse loading system, a temperature control system, and a servo control system.

[0034] The described hydraulic pulse loading system includes an oil source, a stop valve I 24, an accumulator 23, a rotary valve 10, a servo motor 11, a variable damping orifice I 12, a check valve II 13, a booster cylinder 14, and a test piece 20; the oil source includes a main oil tank 6, a hydraulic pump I 1, a check valve I 25, a relief valve I 8, and a reversing valve II 7; the inlet of the hydraulic pump I 1 is connected to the main oil tank 6, the outlet of the hydraulic pump I 1 is connected to the rotary valve 10 through a pipeline and a check valve I 25, and an accumulator 23, a relief valve I 8, a temperature control system, and a pressure relief reversing valve II 7 are connected in parallel between the hydraulic pump I 1 and the rotary valve 10. The rotary valve 10 is respectively connected to the low-pressure chamber of the booster cylinder 14 through a variable damping orifice 12 and a check valve III 13. A temperature sensor I 15 and a pressure sensor 16 are respectively arranged at the inlet of the low-pressure end and the outlet of the high-pressure end of the booster cylinder 14. The booster cylinder 14 is connected to the test piece 20 through a pipeline. A temperature sensor 18 and a makeup oil circuit are arranged at the inlet of the test piece 20. The outlet of the test piece 20 is connected to the inlet of a radiator II 20 through a pipeline. The outlet of the radiator II 22 is connected to an auxiliary oil tank 28; after the stop valve I 24 is opened, the accumulator 23 is pressurized by the hydraulic pump I 1. At the same time, the rotary valve 10 is in the middle position. Since the rotary valve 10 adopts an H-type middle position function, the piston of the booster cylinder 14 moves to the rightmost end of the booster cylinder. Under the control of the servo motor 11, when the rotary valve 10 rotates to the left position, the oil discharged instantaneously from the accumulator 23 is pressurized by the booster cylinder 14 to generate a certain pressure impact on the test piece 20. Subsequently, the accumulator 23 and the hydraulic pump I 1 supply pressure simultaneously, enabling the test piece to bear the rated working pressure. As the rotary valve rotates to the right position, the low-pressure end of the booster cylinder 14 returns to the main oil tank through the variable damping orifice 12 and the temperature control device I. The variable damping orifice 12 provides back pressure for the booster cylinder to prevent oil from flowing back. The pressure of the test piece 20 drops to the pressure value after the back pressure is pressurized by the booster cylinder 14, and the pressure pulse of the oil is the water hammer wave; and as the rotary valve 10 rotates continuously, a periodic water hammer waveform can be formed. The period of this waveform is determined by the rotation speed of the servo motor 11 controlling the rotary valve 10. Additionally, the liquid flow rate instantaneously entering the test piece 20 is controlled by the position and speed of the rotary valve spool, thereby achieving the control of the pressure pulse peak value and the rising rate.

[0035] The described temperature control system includes two parts: a test piece temperature control device and a system temperature control device.

[0036] The temperature control device for the test specimen includes a temperature sensor 18, a controller 17, a variable damping orifice 21, and a radiator II 22. The temperature sensor 18 is arranged at the oil inlet of the test specimen 20, and its signal output end is connected to the signal input end of the controller 17. The signal output end of the controller 17 is connected to the control end of the radiator II 22. This hydraulic hose pulse device simulates the actual working conditions of the hydraulic hose. First, a specific ambient temperature is established. When the device starts to work, the temperature of the oil in the test specimen may not reach this specific ambient temperature. The oil outlet of the test specimen 20 is connected to the variable damping orifice 21. The oil will generate a pressure drop when passing through the variable damping orifice 21, and the pressure drop causes the oil to heat up, increasing the temperature of the oil in the test specimen 20. A temperature sensor 18 is arranged at the oil inlet of the test specimen 20. The temperature sensor 18 collects the temperature signal of the oil in the test specimen 20 and transmits it to the controller 17. The signal output end of the controller 17 is connected to the control end of the radiator II 22. When the temperature of the oil in the test specimen 20 exceeds the set ambient temperature, the controller 17 controls the radiator II 22 to open, maintaining the temperature of the oil in the test specimen 20 near the set ambient temperature.

[0037] The system temperature control device includes a temperature sensor 15, a controller 17, a check valve II 9, a directional control valve I 5, a stop valve II 4, a radiator I 3, and a relief valve II 2. The directional control valve I 5 and the check valve II 9 are in parallel. The port A of the directional control valve I 5 and the check valve II 9 are respectively connected to the oil inlets of the stop valve II 4, the radiator I 3, and the relief valve II 2. The oil outlets of the stop valve II 4, the radiator I 3, and the relief valve II 2 are all connected to the main oil tank 6. The temperature sensor 15 is arranged at the oil inlet of the low-pressure chamber of the intensifier cylinder 14, and its signal output end is connected to the signal input end of the controller 17. The signal output end of the controller 17 is connected to the control end of the stop valve II 4. When this pulse system works, the relief valve I 8 will continuously overflow and generate heat, which will cause the temperature of the oil before the low-pressure end of the intensifier cylinder 14 to rise. Since an excessively high temperature in the hydraulic hose pulse test system will lead to various consequences, including reducing system efficiency, increasing internal leakage in the system, and affecting the pressure pulse waveform, etc. When the temperature signal collected by the temperature sensor 15 exceeds the temperature set value of the controller 17, the controller 17 controls the stop valve 4 to close, and at the same time, the directional control valve I 5 changes to the right position. The radiator I 3 cools the oil overflowed by the relief valve I 8 and the system return oil. The relief valve II 2 is used to protect the radiator I 3. When heat dissipation is not required, the controller 17 controls the stop valve II 4 to close.

[0038] The servo control system includes a pressure sensor 16, a controller 17, a servo motor 11 and a rotary valve 10; the pressure sensor 16 is arranged at the oil outlet of the high-pressure chamber of the booster cylinder 14, and its signal output end is connected to the signal input end of the controller 17. The signal output end of the controller 17 is connected to the control end of the servo motor 11, and the servo motor 11 is mechanically connected to the rotary valve; the pressure pulse signal collected by the pressure sensor is compared with the standard test pulse signal in the controller 17, and the controller 17 adjusts the torque and speed of the servo motor according to the error after comparison to achieve precise control.

[0039] The oil replenishing circuit includes a check valve 19, a hydraulic pump II 27 and a relief valve III 26; the oil outlet of the check valve IV 19 is connected to the oil inlet of the test piece 20, and the oil inlet of the check valve IV 19 is respectively connected to the oil outlet of the hydraulic pump II 27 and the oil inlet of the relief valve III 26. The oil inlets of the hydraulic pump II 27 and the relief valve III 26 are both connected to the auxiliary oil tank 28. The function of the oil replenishing circuit is to replenish oil for the test piece 20 and cooperate with the rotary valve 10 to complete the position adjustment of the booster cylinder 14.

[0040] In the description of the present invention, it should be noted that when terms indicating the orientation or position relationship such as "upper", "lower", "inner", "outer", "left", "right" appear, it should be understood as the orientation or position relationship shown in the drawings, or the orientation or position relationship when the product of the present invention is usually placed during use, or the orientation or position relationship commonly understood by those skilled in the art. It is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or component referred to must have a specific orientation, be constructed and operated in a specific orientation, so it should not be construed as a limitation to the present invention. In addition, when terms such as "first" and "second" appear, they are only used for distinguishing descriptions and cannot be understood as indicating or implying relative importance. In the description of the present invention, it should also be noted that unless otherwise clearly specified and limited, terms such as "installation", "setting", "connection" should be understood in a broad sense. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, and it can be the communication inside two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

Claims

1. A hydraulic hose impact resistance test device based on rotary valve commutation and temperature control, comprising a hydraulic pulse loading system, a temperature control system and a servo control system, characterized in that: The hydraulic pulse loading system includes an oil source, a stop valve I (24), an accumulator (23), a rotary valve (10), a servo motor (11), a variable damping orifice I (12), a check valve II (13), and a booster cylinder (14); The oil source includes a main oil tank (6), a hydraulic pump I (1), a check valve I (25), a relief valve I (8), and a directional control valve II (7), The temperature control system includes a test piece temperature control system and a system temperature test system; The servo control system includes a pressure sensor (16), a controller (17), a servo motor (11), and a rotary valve (10).

2. The hydraulic hose impact resistance test device based on rotary valve commutation and temperature control according to claim 1, characterized in that: A stop valve I (24) is provided at the oil inlet of the accumulator.

3. The hydraulic hose impact resistance test device based on rotary valve commutation and temperature control according to claim 1, characterized in that: The directional control valve II (7) is connected in parallel with the hydraulic pump I (1) and serves as a pressure relief valve.

4. The hydraulic hose impact resistance test device based on rotary valve commutation and temperature control according to claim 1, characterized in that: The rotary valve (10) is servo-controlled by a servo motor (11).

5. The hydraulic hose impact resistance test device based on rotary valve commutation and temperature control according to claim 1, characterized in that: The variable damping orifice (12) can provide back pressure for the booster cylinder (14) to prevent oil from flowing back.

6. The hydraulic hose impact resistance test device based on rotary valve commutation and temperature control according to claim 1, characterized in that: The system temperature control system includes a temperature sensor (15), a controller (17), a check valve II (9), a directional control valve I (5), a stop valve II (4), a radiator I (3), and a relief valve II (2). The temperature controller (15) is arranged at the oil inlet of the low-pressure end of the booster cylinder (14). The controller (17) collects the temperature signal of the temperature sensor (15) and controls the opening or closing of the stop valve II (4).

7. The hydraulic hose impact resistance test device based on rotary valve commutation and temperature control according to claim 1, characterized in that: The test piece temperature control system includes a temperature sensor (18), a controller (17), a variable damping orifice (21), and a radiator II (22); the temperature sensor (18) is arranged at the oil inlet of the test piece (20); the oil forms a pressure drop through the variable damping orifice II (21) to generate heat and save energy; the radiator II (22) is controlled by the controller (17).

8. The hydraulic hose impact resistance test device based on rotary valve commutation and temperature control according to claim 1, characterized in that: The servo control system includes a pressure sensor (16), a controller (17), a servo motor (11) and a rotary valve (10); the pressure sensor (16) is arranged at the oil outlet of the high-pressure section of the intensifying cylinder (14); the controller (17) servo-controls the rotary valve (10) by controlling the torque and speed of the servo motor (11) so that the test piece (20) generates a pressure pulse waveform that meets the requirements.

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