CN114526926B - Pulse fatigue loading test method for pump valve cooperative control - Google Patents
Pulse fatigue loading test method for pump valve cooperative control Download PDFInfo
- Publication number
- CN114526926B CN114526926B CN202210158439.1A CN202210158439A CN114526926B CN 114526926 B CN114526926 B CN 114526926B CN 202210158439 A CN202210158439 A CN 202210158439A CN 114526926 B CN114526926 B CN 114526926B
- Authority
- CN
- China
- Prior art keywords
- hydraulic cylinder
- cavity
- loading
- valve
- control
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M17/00—Testing of vehicles
- G01M17/007—Wheeled or endless-tracked vehicles
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M99/00—Subject matter not provided for in other groups of this subclass
- G01M99/002—Thermal testing
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M99/00—Subject matter not provided for in other groups of this subclass
- G01M99/007—Subject matter not provided for in other groups of this subclass by applying a load, e.g. for resistance or wear testing
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
- G01N3/00—Investigating strength properties of solid materials by application of mechanical stress
- G01N3/32—Investigating strength properties of solid materials by application of mechanical stress by applying repeated or pulsating forces
- G01N3/36—Investigating strength properties of solid materials by application of mechanical stress by applying repeated or pulsating forces generated by pneumatic or hydraulic means
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
- G01N2203/00—Investigating strength properties of solid materials by application of mechanical stress
- G01N2203/0001—Type of application of the stress
- G01N2203/001—Impulsive
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
- G01N2203/00—Investigating strength properties of solid materials by application of mechanical stress
- G01N2203/003—Generation of the force
- G01N2203/0042—Pneumatic or hydraulic means
- G01N2203/0048—Hydraulic means
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E30/00—Energy generation of nuclear origin
- Y02E30/30—Nuclear fission reactors
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Health & Medical Sciences (AREA)
- Life Sciences & Earth Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Biochemistry (AREA)
- General Health & Medical Sciences (AREA)
- Immunology (AREA)
- Pathology (AREA)
- Investigating Strength Of Materials By Application Of Mechanical Stress (AREA)
Abstract
The invention discloses a pulse fatigue loading test method for pump valve cooperative control. The loading test method comprises the following steps: the system comprises a valve control pressure pulse servo control subsystem, a pump control position servo control subsystem, a displacement sensor, an adjustable flow hole, an asymmetric loading hydraulic cylinder, a pressure sensor and an automobile radiator workpiece. The valve control pressure pulse servo control subsystem is used for controlling the pressure output by the asymmetric loading hydraulic cylinder, so that fatigue test is carried out on the automobile radiator workpiece; and the piston displacement of the asymmetric loading hydraulic cylinder is controlled by the pump control position servo control subsystem, so that the risk of cylinder collision in the pulse fatigue loading test process is prevented. The invention realizes the pressure and displacement control of the pulse fatigue loading test equipment at the same time, and has the characteristics of safety, stability, high efficiency and high test precision.
Description
Technical Field
The invention belongs to the field of industrial application, and particularly relates to a pump valve cooperative control pulse fatigue loading test method for testing fatigue performance of an automobile radiator.
Background
The automobile radiator is commonly called an automobile water tank and is an important component in an automobile engine cooling system. The performance of the radiator directly influences the heat radiation effect, the dynamic property, the economy and the reliability of the automobile engine, and even the normal operation and the driving safety. In the working process of the engine, high-temperature refrigerating fluid (water glycol solution) flowing in the radiator can rust and corrode the radiator, and the flowing of the refrigerating fluid can generate periodical pressure vibration so as to influence the performance of the radiator. With the development of the automobile industry, higher requirements are put on the working conditions of the radiator. Therefore, the fatigue performance of the radiator is tested by the pulse fatigue loading test, which is very necessary for the fatigue evaluation of the radiator of the automobile.
The loading cylinder of the existing automobile radiator pulse fatigue loading test equipment adopts a sealing structure which is mostly in contact type sealing, namely, the piston of the loading cylinder is in contact sealing with the cylinder wall through a sealing ring. The contact type sealing structure can cause larger starting friction force of the loading cylinder, and the actual fatigue performance of the radiator in a low-pressure environment is difficult to test. In addition, due to creep property of the hydraulic cylinder, the piston of the hydraulic cylinder can slowly move forward in the loading test process, and the risk of cylinder collision is prolonged.
Disclosure of Invention
Aiming at the problems and defects of the existing pulse fatigue loading test method, the invention improves the precision of the pulse fatigue loading test of the automobile radiator, eliminates the risk of cylinder collision of the existing pulse fatigue loading test method in a long-time test environment, and provides the pulse fatigue loading test method with safe and stable operation, high efficiency and high test precision for pump valve cooperative control.
In order to achieve the above object, the present invention provides the following solutions: a pulse fatigue loading test method for pump valve cooperative control comprises the following steps: the valve control pressure pulse servo control subsystem, the adjustable flow hole, the asymmetric loading hydraulic cylinder and the pressure sensor;
the valve control pressure pulse servo control subsystem specifically comprises: the system comprises a pressure pulse signal generator, a pressure controller, a loading servo valve, a hydraulic power source and a first oil tank; the pressure pulse signal generator is connected with the input end of the pressure controller, the feedback end of the pressure controller is connected with the pressure sensor, and the output end of the pressure controller is connected with the electromagnet of the loading servo valve; the loading servo valve is provided with P, T, A and B four working oil ports, the P port of the loading servo valve is connected with the hydraulic power source, the T port of the loading servo valve is connected with the first oil tank, the A port of the loading servo valve is connected with the A cavity of the asymmetric loading hydraulic cylinder through an oil way, and the B port of the loading servo valve is connected with the B cavity of the asymmetric loading hydraulic cylinder through an oil way;
the asymmetric loading hydraulic cylinder comprises A, B, C and D four chambers, the diameters of a piston rod of a chamber A, a piston rod of a chamber B and a piston rod of a chamber C are the same, a gap is sealed between a piston of the chamber D and a cylinder wall, media of the chamber A and the chamber B of the asymmetric loading hydraulic cylinder are hydraulic oil, loading media of the chamber C and the chamber D are refrigerating fluid, the chamber D of the asymmetric loading hydraulic cylinder is connected with an automobile radiator workpiece through an oil way, and the chamber C of the asymmetric loading hydraulic cylinder is connected with the chamber D of the asymmetric loading hydraulic cylinder through an adjustable flow hole; the pressure sensor is arranged at the outlet of the cavity D of the asymmetric loading hydraulic cylinder and used for detecting a pressure electric signal output at the outlet of the cavity D of the asymmetric loading hydraulic cylinder. The automobile radiator workpiece is a common automobile radiator, and the loading medium in the workpiece is refrigerating fluid (water glycol solution). The valve control pressure pulse servo control subsystem is used for controlling the pressure output by the asymmetric loading hydraulic cylinder, so that fatigue test is performed on the automobile radiator workpiece, the sealing structure of the loading hydraulic cylinder of the pulse fatigue loading test equipment is changed, and therefore the precision of the pulse fatigue loading test of the automobile radiator is improved.
The pulse fatigue loading test method for cooperative control of the pump valve further comprises a pump control position servo control subsystem and a displacement sensor, wherein the pump control position servo control subsystem specifically comprises the following steps: the device comprises a first safety valve, a second oil tank, a second safety valve, a gear pump, a servo motor, a position controller and a position signal generator; the gear pump has P A And P B Two working oil ports, P of the gear pump A The oil port is connected with the cavity A of the asymmetric loading hydraulic cylinder through an oil way, and the gear pump is P B The oil port is connected with the cavity B of the asymmetric loading hydraulic cylinder through an oil way; the first safety valve and the second safety valve are connected in reverse series and then connected to P of a gear pump A Oil port and P B The second oil tank is connected with oil outlets of the first safety valve and the second safety valve; an output shaft of the servo motor is mechanically connected with an input shaft of the gear pump; the position signal generator is connected with the input end of the position controller, the feedback end of the position controller is connected with the displacement sensor, and the output end of the position controller is connected with the control end of the servo motor; the displacement sensor is arranged at the non-partAnd the piston rod connected with the cavity B and the cavity C of the symmetrical loading hydraulic cylinder is used for detecting the position electric signal output by the asymmetrical loading hydraulic cylinder.
When the system performs pulse fatigue loading test, the control mode of the pump control position servo control subsystem is as follows: the position signal generator generates a position command, the command input end of the position controller receives the position command generated by the position signal generator, the command feedback end of the position controller receives a position signal of the asymmetric loading hydraulic cylinder fed back by the displacement sensor, the position controller generates a speed control signal based on a corresponding control algorithm to control the rotating speed of the servo motor so as to control the displacement of the gear pump, thereby realizing the control of the flow of hydraulic oil flowing into/out of an A cavity and a B cavity of the asymmetric loading hydraulic cylinder, further controlling the piston displacement of the asymmetric loading hydraulic cylinder, ensuring that the piston displacement of the asymmetric loading hydraulic cylinder is not greatly deviated near the position command generated by the position signal generator, and excluding the risk of cylinder collision under a long-time test environment.
According to the pulse fatigue loading test method for the cooperative control of the pump valve, before pulse fatigue loading test is conducted on an automobile radiator workpiece, the asymmetric loading hydraulic cylinder is pre-charged, specifically, a triangular wave position command is generated by the position signal generator, the command input end of the position controller receives the position command generated by the position signal generator, the command feedback end of the position controller receives a position signal of a piston of the asymmetric loading hydraulic cylinder fed back by the displacement sensor, the position controller generates a speed control signal based on a corresponding control algorithm, the rotating speed of the servo motor is controlled, the displacement of the gear pump is controlled, the flow of hydraulic oil flowing into/out of an A cavity and a B cavity of the asymmetric loading hydraulic cylinder is controlled, the piston displacement of the asymmetric loading hydraulic cylinder is further controlled, and accordingly the piston of the asymmetric loading hydraulic cylinder is controlled to move from the bottom end to the top end and then returns to the bottom end, and good performance of the asymmetric loading hydraulic cylinder is ensured.
According to the pulse fatigue loading test method for the cooperative control of the pump valve, the gap between the D cavity piston and the cylinder wall of the asymmetric loading hydraulic cylinder is 1 wire.
According to the pulse fatigue loading test method for the cooperative control of the pump valve, the gear pump of the pump control position servo control subsystem is a universal symmetrical hydraulic pump.
Compared with the prior art, the invention has the beneficial effects that:
the invention provides a pulse fatigue loading test method for pump valve cooperative control, which improves the precision of the pulse fatigue loading test of an automobile radiator by changing the sealing structure of a loading hydraulic cylinder of pulse fatigue loading test equipment; by introducing the servo control subsystem at the pumping position, the control can be provided and corrected when the loading hydraulic cylinder of the pulse fatigue loading test equipment is far away from the set position, so that the damage to equipment and automobile radiator workpieces caused by other extreme conditions such as cylinder collision and the like is avoided. The invention realizes the pressure and displacement control of the pulse fatigue loading test equipment at the same time, and has the characteristics of safety, stability, high efficiency and high test precision.
Drawings
FIG. 1 is a hydraulic schematic diagram of a pulse fatigue loading test method for pump valve cooperative control of the present invention; in the figure, a 1-pressure pulse signal generator, a 2-pressure controller, a 3-loading servo valve, a 4-hydraulic power source, a 5-first oil tank, a 6-I safety valve, a 7-second oil tank, an 8-II safety valve, a 9-gear pump, a 10-servo motor, a 11-position controller, a 12-position signal generator, a 13-displacement sensor, a 14-adjustable flow hole, a 15-asymmetric loading hydraulic cylinder, a 16-pressure sensor and a 17-automobile radiator workpiece are arranged.
Fig. 2-7 are graphs of tracking effects of the command signals and the pressure signals at the outlet of the D cavity of the asymmetric loading hydraulic cylinder acquired by the pressure sensor and piston displacement curves of the asymmetric loading hydraulic cylinder acquired by the displacement sensor when the corresponding hydraulic system is built on the AMESim simulation platform and the pressure pulse signal generator generates the command signals with different frequencies, different amplitudes and different types.
FIG. 2 is a graph showing the effect of tracking the command signal and the pressure signal at the outlet of the D cavity of the asymmetric loading hydraulic cylinder acquired by the pressure sensor under the control of the valve-controlled pressure pulse servo control subsystem when the pressure pulse signal generator generates a sinusoidal command signal of 0.1-2bar-1 Hz.
FIG. 3 is a graph showing the piston displacement of an asymmetrically loaded hydraulic cylinder, as captured by a displacement sensor, under control of a pump control position servo control subsystem, when a pressure pulse signal generator generates a sinusoidal command signal of 0.1-2bar-1 Hz.
FIG. 4 is a graph showing the effect of tracking the command signal and the pressure signal at the outlet of the D cavity of the asymmetric loading hydraulic cylinder acquired by the pressure sensor under the control of the valve-controlled pressure pulse servo control subsystem when the pressure pulse signal generator generates a sinusoidal command signal of 0.1-4bar-2 Hz.
FIG. 5 is a graph showing the piston displacement of an asymmetrically loaded hydraulic cylinder, as captured by a displacement sensor, under control of a pump control position servo control subsystem, when a pressure pulse signal generator generates a sinusoidal command signal of 0.1-4bar-2 Hz.
FIG. 6 is a graph showing the effect of tracking the command signal and the pressure signal at the outlet of the D cavity of the asymmetric loading hydraulic cylinder acquired by the pressure sensor under the control of the valve-controlled pressure pulse servo control subsystem when the pressure pulse signal generator generates a trapezoidal command signal of 0.1-4bar-1 Hz.
FIG. 7 is a graph showing the piston displacement of an asymmetrically loaded hydraulic cylinder, as captured by a displacement sensor, under control of a pump control position servo control subsystem, when a pressure pulse signal generator generates a trapezoidal command signal of 0.1-4bar-1 Hz.
Detailed Description
The invention is further explained below with reference to the drawings.
The invention aims to provide a pulse fatigue loading test method for pump valve cooperative control, which improves the pulse fatigue loading test precision of an automobile radiator and simultaneously eliminates the risk of cylinder collision possibly caused in the pulse fatigue loading test process.
As shown in fig. 1, a pulse fatigue loading test method for pump valve cooperative control includes: the system comprises a valve control pressure pulse servo control subsystem, a pump control position servo control subsystem, a displacement sensor 13, an adjustable flow hole 14, an asymmetric loading hydraulic cylinder 15, a pressure sensor 16 and an automobile radiator workpiece 17.
The valve control pressure pulse servo control subsystem consists of a pressure pulse signal generator 1, a pressure controller 2, a loading servo valve 3, a hydraulic power source 4 and a first oil tank 5, wherein the pressure pulse signal generator 1 can generate various loading command signals such as sine, trapezoid, multi-order, triangle and the like according to specific requirements; the pressure pulse signal generator 1 is connected with the input end ("+") of the pressure controller 2, the feedback end ("-") of the pressure controller 2 is connected with the pressure sensor 16, and the output end of the pressure controller 2 is connected with the electromagnet for loading the servo valve 3; the loading servo valve 3 is provided with P, T, A and four working oil ports B, the port P of the loading servo valve 3 is connected with the hydraulic power source 4, the port T of the loading servo valve 3 is connected with the first oil tank 5, the port A of the loading servo valve 3 is connected with the cavity A of the asymmetric loading hydraulic cylinder 15 through an oil way, and the port B of the loading servo valve 3 is connected with the cavity B of the asymmetric loading hydraulic cylinder 15 through an oil way;
the pump control position servo control subsystem consists of a first safety valve 6, a second oil tank 7, a second safety valve 8, a gear pump 9, a servo motor 10, a position controller 11 and a position signal generator 12, wherein the gear pump 9 is provided with a P A And P B Two working oil ports, P of gear pump 9 A The oil port is connected with the A cavity of the asymmetric loading hydraulic cylinder 15 through an oil way, and the P of the gear pump 9 B The oil port is connected with the cavity B of the asymmetric loading hydraulic cylinder 15 through an oil way; the first safety valve 6 and the second safety valve 8 are connected in reverse series and then connected with P of a gear pump 9 A Oil port and P B The second oil tank 7 is connected with oil outlets of the first safety valve 6 and the second safety valve 8; an output shaft of the servo motor 10 is mechanically connected with an input shaft of the gear pump 9; the position signal generator 12 is connected with an input end ("+") of the position controller 11, a feedback end ("-") of the position controller 11 is connected with the displacement sensor 13, and an output end of the position controller 11 is connected with a control end of the servo motor 10;
the asymmetric loading hydraulic cylinder 15 comprises A, B, C and D four chambers, wherein the A chamber of the asymmetric loading hydraulic cylinder 15 is communicated with the oil pathP with port a of the loading servo valve 3 and gear pump 9 respectively A The oil port is connected with the cavity B of the asymmetric loading hydraulic cylinder 15 and is respectively connected with the port B of the loading servo valve 3 and the port P of the gear pump 9 through oil paths B The oil port is connected with a D cavity of the asymmetric loading hydraulic cylinder 15, the D cavity of the asymmetric loading hydraulic cylinder 15 is connected with an automobile radiator workpiece 17 through an oil way, and a C cavity of the asymmetric loading hydraulic cylinder 15 is connected with a D cavity of the asymmetric loading hydraulic cylinder 15 through an adjustable flow hole 14; the displacement sensor 13 is arranged on a piston rod connected with the cavity B and the cavity C of the asymmetric loading hydraulic cylinder 15 and is used for detecting a position electric signal output by the asymmetric loading hydraulic cylinder 15; the pressure sensor 16 is disposed at an outlet of the D-chamber of the asymmetric loading hydraulic cylinder 15, and is configured to detect a pressure electric signal at the outlet of the D-chamber of the asymmetric loading hydraulic cylinder 15.
The pressure pulse signal of the pressure pulse signal generator 1 and the position signal of the position signal generator 12 can be controlled and generated by an upper computer at a PC end, the pressure controller 2 and the position controller 11 adopt a simple PID control algorithm, the loading servo valve 3 adopts a high-frequency response flow servo valve, the I safety valve 6 and the II safety valve 8 adopt overflow valves, the gear pump 9 adopts a gear pump with fixed displacement, the servo motor 10 adopts an alternating current servo motor, the asymmetric loading hydraulic cylinder 15 adopts an asymmetric single booster cylinder, media of an A cavity and a B cavity of the asymmetric loading hydraulic cylinder 15 are hydraulic oil, media of a C cavity and a D cavity are refrigerating fluid (water glycol solution), the displacement sensor 13 adopts a magnetostriction displacement sensor, the pressure sensor 16 adopts a piezoresistive pressure sensor, and a loading medium in the automobile radiator workpiece 17 is refrigerating fluid (water glycol solution).
For safety and loading requirements, before the pulse fatigue loading test is performed on the automobile radiator workpiece 17, the asymmetric loading hydraulic cylinder 15 is pre-charged, specifically, a triangular wave position command is generated by the position signal generator 12, a command input end ("+" end) of the position controller 11 receives the position command generated by the position signal generator 12, a command feedback end ("-" end) of the position controller 11 receives a position signal of a piston of the asymmetric loading hydraulic cylinder 15 fed back by the displacement sensor 13, the position controller 11 generates a speed control signal based on a corresponding control algorithm (PID control algorithm), controls the rotating speed of the servo motor 10, further controls the displacement of the gear pump 9, and further controls the piston displacement of the asymmetric loading hydraulic cylinder 15, so that the piston of the asymmetric loading hydraulic cylinder 15 is controlled to move from the bottom end to the top end and returns to the bottom end, and good performance of the asymmetric loading hydraulic cylinder 15 is ensured.
When the system performs pulse fatigue loading test, the control mode of the valve control pressure pulse servo control subsystem is as follows: the pressure pulse signal generator 1 generates a pressure command signal which is expected to track, the command input end ("+" end) of the pressure controller 2 receives the pressure command signal which is expected to track and generated by the pressure pulse signal generator 1, the command feedback end ("-" end) of the pressure controller 2 receives the pressure signal at the outlet of the D cavity of the asymmetric loading hydraulic cylinder 15 fed back by the pressure sensor 16, the pressure controller 2 generates a control signal based on a corresponding control algorithm (PID control algorithm), the control of the flow rate of hydraulic oil flowing into/out of the A cavity and the B cavity of the asymmetric loading hydraulic cylinder 15 is realized by controlling the valve core displacement of the loading servo valve 3, and then the control of the pressure at the outlet of the D cavity of the asymmetric loading hydraulic cylinder 15 is realized, so that the pressure value of refrigerating fluid (water glycol solution) flowing into the automobile radiator workpiece 17 can well track the pressure command signal which is expected to track and generated by the pressure pulse signal generator 1.
When the system performs pulse fatigue loading test, the control mode of the pump control position servo control subsystem is as follows: the position signal generator 12 generates a position command, the command input end ("+" end) of the position controller 11 receives the position command generated by the position signal generator 12, the command feedback end ("-" end) of the position controller 11 receives the position signal of the asymmetric loading hydraulic cylinder 15 fed back by the displacement sensor 13, the position controller 11 generates a speed control signal based on a corresponding control algorithm (PID control algorithm), controls the rotating speed of the servo motor 10, further controls the displacement of the gear pump 9, realizes the control of the flow rate of hydraulic oil flowing into/out of the A cavity and the B cavity of the asymmetric loading hydraulic cylinder 15, further controls the piston displacement of the asymmetric loading hydraulic cylinder 15, and ensures that the piston displacement of the asymmetric loading hydraulic cylinder 15 does not deviate greatly near the position command generated by the position signal generator 12.
In the above embodiment of the present invention, the valve-controlled pressure pulse servo control subsystem and the pump-controlled position servo control subsystem respectively operate, and simultaneously control the flow rate of hydraulic oil flowing into/out of the a cavity and the B cavity of the asymmetric loading hydraulic cylinder 15, thereby realizing control of the pressure at the outlet of the D cavity of the asymmetric loading hydraulic cylinder 15 and the piston displacement of the asymmetric loading hydraulic cylinder 15. Wherein the valve control pressure pulse servo control subsystem plays a main control role, and the pump control position servo control subsystem plays an auxiliary control role.
By adjusting the opening of the adjustable orifice 14, the generation of negative pressure in the C-chamber of the asymmetric loading cylinder 15 during the pulse fatigue loading test can be avoided.
Fig. 2, 4 and 6 show graphs of the effect of the tracking of the command signal (solid line) with the pressure signal (broken line) at the outlet of the D-chamber of the asymmetrically loaded cylinder 15 acquired by the pressure sensor 16, when the pressure pulse signal generator 1 generates command signals of different frequencies, different amplitudes and different types. From the trace effect map, it can be seen that: for different command signals, under the control of the valve control pressure pulse servo control subsystem, the tracking pressure curve of the scheme can reach the peak value and the trough value of the command signals, the tracking effect is good, and the curve is not distorted.
Fig. 3, 5 and 7 show the piston displacement curves of the asymmetric loading cylinder 15 acquired by the displacement sensor 13 when the pressure pulse signal generator 1 generates command signals of different frequencies, different amplitudes and different types. From the trace effect map, it can be seen that: for different working conditions, under the control of the pump control position servo control subsystem, the piston displacement curve of the asymmetric loading hydraulic cylinder 15 is kept stable and cannot deviate.
Claims (5)
1. The pulse fatigue loading test method for pump valve cooperative control is characterized by comprising the following steps of: the system comprises a valve control pressure pulse servo control subsystem, an adjustable flow hole (14), an asymmetric loading hydraulic cylinder (15) and a pressure sensor (16);
the valve control pressure pulse servo control subsystem specifically comprises: the device comprises a pressure pulse signal generator (1), a pressure controller (2), a loading servo valve (3), a hydraulic power source (4) and a first oil tank (5); the pressure pulse signal generator (1) is connected with the input end of the pressure controller (2), the feedback end of the pressure controller (2) is connected with the pressure sensor (16), and the output end of the pressure controller (2) is connected with the electromagnet of the loading servo valve (3); the loading servo valve (3) is provided with P, T, A and four working oil ports B, the port P of the loading servo valve (3) is connected with the hydraulic power source (4), the port T of the loading servo valve (3) is connected with the first oil tank (5), the port A of the loading servo valve (3) is connected with the cavity A of the asymmetric loading hydraulic cylinder (15) through an oil way, and the port B of the loading servo valve (3) is connected with the cavity B of the asymmetric loading hydraulic cylinder (15) through an oil way;
the asymmetric loading hydraulic cylinder (15) comprises A, B, C and D four chambers, the diameters of a piston rod of a cavity A, a piston rod of a cavity B and a piston rod of a cavity C are the same, a gap is sealed between a piston of the cavity D and a cylinder wall, media of the cavity A and the cavity B of the asymmetric loading hydraulic cylinder (15) are hydraulic oil, loading media of the cavity C and the cavity D are refrigerating fluid, the cavity D of the asymmetric loading hydraulic cylinder is connected with an automobile radiator workpiece (17) through an oil way, and the cavity C of the asymmetric loading hydraulic cylinder is connected with the cavity D of the asymmetric loading hydraulic cylinder through an adjustable flow hole (14); the pressure sensor (16) is arranged at the outlet of the cavity D of the asymmetric loading hydraulic cylinder and used for detecting a pressure electric signal output at the outlet of the cavity D of the asymmetric loading hydraulic cylinder.
2. The pulse fatigue loading test method for pump valve cooperative control according to claim 1, wherein the pulse fatigue loading test method is characterized by comprising the following steps of: the system also comprises a pump control position servo control subsystem and a displacement sensor (13), wherein the pump control position servo control subsystem specifically comprises: the first safety valve (6), the second oil tank (7) and the second safety valve8) The device comprises a gear pump (9), a servo motor (10), a position controller (11) and a position signal generator (12); the gear pump (9) has P A And P B Two working oil ports, P of the gear pump (9) A The oil port is connected with the A cavity of the asymmetric loading hydraulic cylinder (15) through an oil way, and the P of the gear pump (9) B The oil port is connected with a cavity B of the asymmetric loading hydraulic cylinder (15) through an oil way; the first safety valve (6) and the second safety valve (8) are connected in reverse series and then connected with P of a gear pump (9) A Oil port and P B The second oil tank (7) is connected with oil outlets of the first safety valve (6) and the second safety valve (8); an output shaft of the servo motor (10) is mechanically connected with an input shaft of the gear pump (9); the position signal generator (12) is connected with the input end of the position controller (11), the feedback end of the position controller (11) is connected with the displacement sensor (13), and the output end of the position controller (11) is connected with the control end of the servo motor (10); the displacement sensor (13) is arranged on a piston rod connected with the cavity B and the cavity C of the asymmetric loading hydraulic cylinder and used for detecting a position electric signal output by the asymmetric loading hydraulic cylinder.
3. The pulse fatigue loading test method for pump valve cooperative control according to claim 2, wherein the pulse fatigue loading test method is characterized by comprising the following steps of: before pulse fatigue loading test is carried out on an automobile radiator workpiece (17), the asymmetric loading hydraulic cylinder (15) is pre-charged, specifically, a triangular wave position command is generated by the position signal generator (12), a command input end of the position controller (11) receives the position command generated by the position signal generator (12), a command feedback end of the position controller (11) receives a position signal of a piston of the asymmetric loading hydraulic cylinder (15) fed back by the displacement sensor (13), the position controller (11) generates a speed control signal based on a corresponding control algorithm, the rotating speed of the servo motor (10) is controlled, the displacement of the gear pump (9) is controlled, the flow of hydraulic oil flowing into/out of an A cavity and a B cavity of the asymmetric loading hydraulic cylinder (15) is controlled, the piston displacement of the asymmetric loading hydraulic cylinder (15) is further controlled, and accordingly, the piston of the asymmetric loading hydraulic cylinder (15) is controlled to move from the bottom end to the top end, and good performance of the asymmetric loading hydraulic cylinder (15) is ensured.
4. A pump valve cooperative control pulse fatigue loading test method according to claim 1, 2 or 3, wherein: the clearance between the D cavity piston and the cylinder wall of the asymmetric loading hydraulic cylinder is 1 wire.
5. A pump valve coordinated control pulse fatigue loading test method according to claim 2 or 3, characterized in that: the gear pump (9) of the pump control position servo control subsystem is a universal symmetrical hydraulic pump.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210158439.1A CN114526926B (en) | 2022-02-21 | 2022-02-21 | Pulse fatigue loading test method for pump valve cooperative control |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210158439.1A CN114526926B (en) | 2022-02-21 | 2022-02-21 | Pulse fatigue loading test method for pump valve cooperative control |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114526926A CN114526926A (en) | 2022-05-24 |
| CN114526926B true CN114526926B (en) | 2023-06-16 |
Family
ID=81625613
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210158439.1A Active CN114526926B (en) | 2022-02-21 | 2022-02-21 | Pulse fatigue loading test method for pump valve cooperative control |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114526926B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116973094A (en) * | 2023-08-01 | 2023-10-31 | 武汉万曦智能科技有限公司 | Automatic test control system for safety valve |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2021004397A1 (en) * | 2019-07-09 | 2021-01-14 | 中国矿业大学 | Large flow valve-pump joint control emulsion pump station and control method therefor |
| CN113790975A (en) * | 2021-09-14 | 2021-12-14 | 吉林大学 | Ultrasonic amplitude transformer assembly, ultrasonic fatigue loading test device and test method |
-
2022
- 2022-02-21 CN CN202210158439.1A patent/CN114526926B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2021004397A1 (en) * | 2019-07-09 | 2021-01-14 | 中国矿业大学 | Large flow valve-pump joint control emulsion pump station and control method therefor |
| CN113790975A (en) * | 2021-09-14 | 2021-12-14 | 吉林大学 | Ultrasonic amplitude transformer assembly, ultrasonic fatigue loading test device and test method |
Non-Patent Citations (3)
| Title |
|---|
| 基于泵阀协调控制的电液位置伺服节能控制研究;刘华等;《机电工程》;全文 * |
| 泵阀并联电液位置伺服系统的智能控制方法;汪成文等;《华南理工大学学报（自然科学版）》;全文 * |
| 矿用车辆车架疲劳试验台加载系统设计;杨平;李维嘉;蒋跃辉;;液压与气动(03);全文 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN114526926A (en) | 2022-05-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN114526926B (en) | Pulse fatigue loading test method for pump valve cooperative control | |
| CN102564860B (en) | Rotating joint durability testing principle and full-automatic testing machine | |
| CN202195990U (en) | Impulse cycle-testing apparatus | |
| KR20060117577A (en) | Hybrid actuator system of electric-hydraulic united control type | |
| CN107676272A (en) | A kind of fast adjuster of Working Conditions of Centrifugal Injection Pumps | |
| AU2010276482B2 (en) | Hydraulic power module | |
| CN112697439B (en) | Complete machine liquid flow test system and method for electric pump circulation rocket engine | |
| CN104100508A (en) | Use of a motor-driven speed-variable hydraulic pump as a hydrostatic transmission | |
| ES8501051A1 (en) | Compact electro-hydraulic actuator for turbine valves. | |
| CN100507330C (en) | High volume gas pressure regulating valve | |
| JP2004301188A (en) | Hydraulic control system | |
| CN105644619A (en) | Intelligent hydraulic power steering system and control method thereof | |
| CN214945442U (en) | Hydraulic motor test hydraulic system | |
| CN105508322A (en) | Pump control type hydraulic retarding system and control method thereof | |
| CN212225499U (en) | Hydraulic positive and negative pressure test system | |
| CN114754944A (en) | Positive/negative pressure dynamic sealing performance test platform | |
| CN111237292B (en) | Speed closed-loop control method of variable-rotation-speed single-pump cylinder control closed system under four-quadrant working condition | |
| CN111927904A (en) | Constant speed reduction controllable hydraulic retarder | |
| CN212564656U (en) | Self-oil-supply integrated speed regulating system | |
| CN105539578A (en) | Direct-current brushless electro-hydraulic power steering pump and control method thereof of new energy passenger car | |
| CN112049981A (en) | Self-oil-supply integrated speed regulating system | |
| CN210487486U (en) | Intelligent servo hydraulic source system applied to material mechanics testing machine | |
| CN105545490A (en) | Closed-loop gas turbine hydraulic starting method and gas turbine hydraulic system | |
| CN109765016B (en) | Method and device for testing axial dynamic stiffness of main shaft | |
| RU2815567C1 (en) | Control method of electrohydraulic servo drive with machine-throttle control |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |