CN113482872B - Intelligent aviation variable plunger pump pressure flow self-adaptive control system - Google Patents

Intelligent aviation variable plunger pump pressure flow self-adaptive control system Download PDF

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CN113482872B
CN113482872B CN202110833508.XA CN202110833508A CN113482872B CN 113482872 B CN113482872 B CN 113482872B CN 202110833508 A CN202110833508 A CN 202110833508A CN 113482872 B CN113482872 B CN 113482872B
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pressure
displacement
closed
value
variable
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CN113482872A (en
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欧阳小平
杨波
方华
蒋昊宜
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Zhejiang University ZJU
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Zhejiang University ZJU
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Computer Hardware Design (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

The invention discloses an intelligent aviation variable plunger pump pressure flow self-adaptive control system which comprises a motor, a variable plunger pump, a servo valve, a valve core displacement sensor, a swash plate displacement LVDT sensor, a pressure sensor, a controller, a pressurizing oil tank and a shell, wherein the variable plunger pump is provided with a variable piston main cylinder, the output end of the motor is connected with the variable plunger pump, the variable piston main cylinder is moved by oil of the servo valve, the controller receives valve core displacement Sa1, swash plate displacement Sa2, actual pressure Pa, actual current Ia, a pressure instruction Pc, a displacement instruction Vc and a power instruction Wc, and the instruction current Ic is output to an electromagnet of the servo valve through operation. The invention adopts triple closed-loop control, thus improving the control precision of the aviation pump; limiting the pump output power by the product of the limiting pressure and flow; the pressure and flow self-adaptive selector is adopted, the flow pressure control is automatically switched, overflow heating is avoided, and the efficiency of the aviation pump is improved.

Description

Intelligent aviation variable plunger pump pressure flow self-adaptive control system
Technical Field
The invention relates to the field of plunger pump control, in particular to an intelligent aviation variable plunger pump pressure flow self-adaptive control system.
Background
The variable displacement piston pump is a hydraulic pump capable of stepless regulating its output displacement by controlling the inclination direction and angle of its variable mechanism-swash plate. The variable plunger pump has the characteristics of high volumetric efficiency, stable operation, good flow uniformity, low noise and high working pressure, so that the variable plunger pump is applied to more and more occasions. The aviation pump is a core component in an aircraft control system, and due to the working conditions of narrow space, poor heat dissipation condition and the like, the aviation pump needs to have the characteristics of small size, high power, capability of obtaining high speed and high power density, strong and firm impact resistance, strong environmental resistance, long service life and the like. Traditional aviation pump is subject to the restriction of size, generally makes the constant delivery pump, changes the output flow of pump through the rotational speed that changes the motor, and this kind of structural advantage lies in simple structure, and weight is lighter, nevertheless because integrates the degree higher, leads to its heat dissipation comparatively difficult, and the situation of generating heat is comparatively serious, hardly realizes the best of performance such as efficiency, dynamic characteristic and power-to-weight ratio simultaneously.
Therefore, the aviation pump is necessary to adopt a variable plunger form, but the microminiaturization trend of the aviation pump increases the difficulty of controlling the aviation pump, and the high-end application places also put higher requirements on the robustness and the precision of the aviation variable pump. Because of the requirements of size limitation and high power density, the efficiency is also a factor which cannot be ignored, and one mode of controlling the outlet pressure of the traditional hydraulic pump is to use an overflow valve, and the other mode is to add a constant pressure valve. The overflow can appear very obviously in the first mode and generate heat, reduces system efficiency, is not suitable for the aviation pump, and the overflow can be reduced to a certain extent to the mode that the constant pressure valve was added to the second kind, but when the pressure that the system needs did not reach the pressure that the constant pressure valve set for, the pump can be exported with maximum flow, and under this kind of operating mode, the flow that surpasss also can lead to extra overflow loss.
Therefore, how to realize configuration, innovation and control strategy innovation, the traditional control mode is improved, and the control with high robustness, high precision and high efficiency is realized, which is the key and difficult point of the future development of the intelligent aviation pump control.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide an intelligent adaptive control system for the pressure and the flow of an aviation variable plunger pump, so that the robustness of the pump control is improved, and the adaptive control system is subjected to adaptive switching in a flow pressure mode; according to the control method, when the system reaches the set pressure, the pump enters the pressure ring, the set pressure is maintained, the pump displacement can return to be close to the minimum, leakage of the pump is maintained, when the system pressure does not reach the set pressure, the pump enters the flow ring, the set flow is maintained, extra overflow loss is avoided, and the efficiency of the pump is improved; and a triple inner closed loop is adopted, so that the pump control precision is improved, the overshoot is reduced, and the static error is reduced.
The scheme for solving the technical problems is as follows:
the pressure and flow self-adaptive control system comprises a motor, a variable plunger pump, a servo valve, a valve element displacement sensor for detecting the valve element displacement of the servo valve, a swash plate displacement LVDT sensor, a pressure sensor for detecting the outlet pressure of the variable plunger pump, a controller, a pressurizing oil tank for supplying oil to the variable plunger pump and a shell, wherein the variable plunger pump is provided with a variable piston main cylinder and a variable piston auxiliary cylinder, the output end of the motor is connected with the variable plunger pump, oil drainage of the variable plunger pump and oil at a T port of the servo valve return to the shell, the variable piston main cylinder is moved by the oil of the servo valve, the swash plate displacement LVDT sensor is used for detecting the displacement of the variable piston main cylinder, and the controller receives the valve element displacement Sa1 of the valve element displacement sensor, the swash plate displacement 2 of the swash plate displacement sensor, and the actual pressure Pa, Sa1, Sa of the pressure sensor, The actual current Ia, the pressure command Pc, the displacement command Vc and the power command Wc of the servo valve are calculated to output a command current Ic to the electromagnet of the servo valve.
The servo valve, the swash plate displacement LVDT sensor and the pressure sensor are all connected to the variable displacement plunger pump, and the spool displacement sensor is installed in the servo valve.
The outlet flow of the variable plunger pump is introduced into a port P of the servo valve and enters the variable piston main cylinder according to the displacement proportion of a valve core of the servo valve, and when the pressure of a rodless cavity of the variable piston main cylinder is greater than the spring force of the variable piston auxiliary cylinder, the displacement of the variable plunger pump is reduced; when the pressure of the rodless cavity of the piston main cylinder is smaller than the spring force of the variable piston secondary cylinder, the displacement of the variable plunger pump is increased.
The swash plate displacement LVDT sensor comprises an LVDT sensor shell, an LVDT sensor inner core, an LVDT sensor protective shell and an LVDT sensor connecting rod, one end of the LVDT sensor connecting rod is connected with a piston of the variable piston master cylinder through threads, the LVDT sensor inner core is installed at the other end of the LVDT sensor connecting rod in an interference fit mode, the LVDT sensor protective shell is connected with a cylinder barrel of the variable piston master cylinder through a fixing bolt, the LVDT sensor protective shell is connected with the LVDT sensor shell through threads, and the LVDT sensor inner core is located in the LVDT sensor shell.
The cylinder barrel of the variable piston master cylinder is sealed with the connecting rod of the LVDT sensor through a Glare ring, and the cylinder barrel of the variable piston master cylinder is sealed with the protective shell of the LVDT sensor through a dustproof O-shaped ring.
The outer wall of the LVDT sensor shell is in threaded connection with a locking nut, the locking nut abuts against the end face of the LVDT sensor protective shell, and signals of the swash plate displacement LVDT sensor are led out through a connecting cable.
The controller comprises a differential voltage amplifier I, a differential voltage amplifier II, a differential voltage amplifier III, a ramp signal generator I, a ramp signal generator II, a divider, a minimum value selector I, a minimum value selector II, an absolute value generator I, an absolute value generator II, a pressure closed-loop controller, a flow closed-loop controller, a pressure flow self-adaptive selector, a valve core displacement closed-loop controller, a current closed-loop controller, a modem I, a modem II, a sensor signal regulator I, a sensor signal regulator II, a sensor signal regulator III, a current-voltage converter and a servo valve driver;
the pressure instruction Pc enters a pressure closed-loop controller through the quantitative conversion of a differential voltage amplifier I and a ramp signal generator I, the actual pressure Pa enters the pressure closed-loop controller through the quantitative conversion of a current-voltage converter and a sensor signal regulator III, and the pressure closed-loop controller generates a pressure closed-loop value through proportional, integral and differential advanced calculation;
dividing a power instruction Wc by a quantized value of actual pressure Pa through quantized conversion of a differential voltage amplifier II, comparing the power instruction Wc with a displacement instruction Vc by the quantized conversion of a differential voltage amplifier III and a ramp signal generator II to carry out minimum value comparison, selecting a smaller value to enter a flow closed-loop controller, enabling a swash plate displacement Sa2 to enter the flow closed-loop controller through the quantized conversion of a modem I and a sensor signal regulator I, and enabling the flow closed-loop controller to generate a flow closed-loop value through proportional, integral and differential calculation;
the pressure closed-loop value and the flow closed-loop value are selected to be in accordance with the requirement through a pressure flow self-adaptive selector and enter a valve core displacement closed-loop controller, the valve core displacement Sa1 enters the valve core displacement closed-loop controller through the quantitative conversion of a modem II and a sensor signal regulator II, and the valve core displacement closed-loop controller generates a voltage instruction value through proportional and differential preceding calculation;
the voltage instruction value is converted into a current value through a servo valve driver and enters a current closed-loop controller, the actual current Ia of the servo valve enters the current closed-loop controller, and the current closed-loop controller generates an instruction current Ic through proportional calculation.
The pressure flow self-adaptive selector comprises a second minimum value selector, a first absolute value generator and a second absolute value generator, wherein the second minimum value selector selects a closed-loop value with a smaller absolute value from the first absolute value generator and the second absolute value generator as an output value.
The controller comprises a divider, a minimum value selector I, a minimum value selector II, an absolute value generator I, an absolute value generator II, a pressure closed-loop controller, a flow closed-loop controller, a pressure flow self-adaptive selector, a valve core displacement closed-loop controller and a current closed-loop controller;
the quantized value of the pressure instruction Pc and the quantized value of the actual pressure Pa enter a pressure closed-loop controller, and the pressure closed-loop controller generates a pressure closed-loop value through calculation;
dividing the quantized value of the power instruction Wc by the quantized value of the actual pressure Pa, performing minimum comparison with the quantized value of the displacement instruction Vc, selecting a smaller value to enter a flow closed-loop controller, and entering the quantized value of the swash plate displacement Sa2 into the flow closed-loop controller, wherein the flow closed-loop controller generates a flow closed-loop value through calculation;
the pressure closed-loop value and the flow closed-loop value are selected to be in accordance with the requirement through a pressure flow self-adaptive selector and enter a valve core displacement closed-loop controller, the quantized value of the valve core displacement Sa1 enters the valve core displacement closed-loop controller, and the valve core displacement closed-loop controller generates a voltage instruction value through calculation;
the quantized value of the voltage instruction value enters a current closed-loop controller, the actual current Ia of the servo valve enters the current closed-loop controller, and the current closed-loop controller generates an instruction current Ic through calculation.
The pressure flow self-adaptive selector comprises a second minimum value selector, a first absolute value generator and a second absolute value generator, wherein the second minimum value selector selects a closed-loop value with a smaller absolute value from the first absolute value generator and the second absolute value generator as an output value.
The invention has the following outstanding effects: the installation structure of the swash plate displacement LVDT sensor of the aviation variable displacement pump avoids the complex mode of adding a slope to change the displacement of the swash plate outside the open hole of the traditional plunger pump shell, skillfully utilizes the installation screw of the pump swash plate, integrates the connecting rod and the small swash plate displacement LVDT sensor, does not obviously increase the mass and the size of the pump, and has the exposed size of only 29mm and the diameter of 12 mm. The invention adopts a current closed loop, a servo valve core position closed loop, a pressure closed loop or a flow closed loop triple closed loop, improves the precision of current, valve core displacement and pressure or flow control layer by layer, eliminates accumulated errors, improves the total control precision and reduces steady-state errors. The invention provides a flow pressure self-adaptive control selector, which can automatically select a pressure closed loop or a flow closed loop under different working conditions, reduces the control complexity, improves the robustness of a system, and simultaneously, because the pressure flow control is realized by controlling the position of a swash plate, oil overflow cannot be generated, and the efficiency of a pump is improved. The invention provides a power limiting strategy to avoid system overload.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic view of the mounting structure of the swash plate displacement LVDT sensor of the present invention;
FIG. 3 is a control framework diagram of the present invention.
In the figure: 1-motor, 2-variable plunger pump, 3-variable piston master cylinder, 4-variable piston slave cylinder, 5-servo valve, 6-spool displacement sensor, 7-swash plate displacement LVDT sensor, 8-pressure sensor, 9-controller, 10-pressurized oil tank, 11-shell, 12.1-differential voltage amplifier I, 12.2-differential voltage amplifier II, 12.3-differential voltage amplifier III, 13.1-ramp signal generator I, 13.2-ramp signal generator II, 14-divider, 15.1-minimum value selector I, 15.2-minimum value selector II, 16.1-absolute value generator I, 16.2-absolute value generator II, 17-pressure closed loop controller, 18-flow closed loop controller, 19-pressure flow adaptive selector, 20-spool displacement closed-loop controller, 21-current closed-loop controller, 22.1-modem I, 22.2-modem II, 23.1-sensor signal regulator I, 23.2-sensor signal regulator II, 23.3-sensor signal regulator III, 24-current-voltage converter, 25-servo valve driver, 26-LVDT sensor connecting rod, 27-Glare ring, 28-fixing bolt, 29-dustproof O-shaped ring, 30-LVDT sensor protecting shell, 31-LVDT sensor shell, 32-LVDT sensor inner core, 33-locking nut and 34-connecting cable.
Detailed Description
The invention is further described with reference to the accompanying drawings and the detailed description below:
example 1:
as shown in fig. 1-3, an intelligent adaptive control system for pressure and flow of an aviation variable displacement plunger pump comprises a motor 1, a variable displacement plunger pump 2, a servo valve 5, a spool displacement sensor 6 for detecting spool displacement of the servo valve 5, a swash plate displacement LVDT sensor 7, a pressure sensor 8 for detecting outlet pressure of the variable displacement plunger pump 2, a controller 9, a pressurized oil tank 10 for supplying oil to the variable displacement plunger pump 2, and a housing 11, wherein the variable displacement plunger pump 2 sucks oil from the pressurized oil tank 10.
The variable plunger pump 2 is provided with a variable piston main cylinder 3 and a variable piston auxiliary cylinder 4, the output end of the motor 1 is connected with the variable plunger pump 2, and the motor 1 is connected with the variable plunger pump 2 through a coupler.
The oil drainage of the variable displacement plunger pump 2 and the oil at the port T of the servo valve 5 return to the shell 11, the variable piston master cylinder 3 is moved by the oil of the servo valve 5, the swash plate displacement LVDT sensor 7 is used for detecting the displacement of the variable piston master cylinder 3, and the controller 9 receives the valve element displacement Sa1 of the valve element displacement sensor 6, the swash plate displacement Sa2 of the swash plate displacement LVDT sensor 7, the actual pressure Pa of the pressure sensor 8, the actual current Ia of the servo valve 5, the pressure command Pc, the displacement command Vc and the power command Wc, and outputs the command current Ic to the electromagnet of the servo valve 5 through calculation.
The valve core displacement sensor 6 collects and transmits a valve core displacement signal Sa1 of the servo valve 5 to the controller 9; the swash plate displacement LVDT sensor 7 collects and transmits a swash plate displacement signal Sa2 of the variable piston master cylinder 3 to the controller 9; the pressure sensor 8 collects and transmits an outlet pressure signal Pa of the variable plunger pump 2 to the controller 9; the current signal Ia of the electromagnet coil of the servo valve 5 is transmitted to the controller 9; meanwhile, the controller 9 receives the pressure command signal Pc, the flow command signal Vc, and the power command signal Wc, and outputs a command current Ic to the servo valve 5 through calculation of an intelligent control method with the feedback signal, thereby completing the displacement control of the variable displacement plunger pump 2.
The servo valve 5, the swash plate displacement LVDT sensor 7 and the pressure sensor 8 are all connected to the variable displacement plunger pump 2, and the spool displacement sensor 6 is installed in the servo valve 5. The servo valve 5 is connected to the variable displacement piston pump 2 through bolts; the valve core displacement sensor 6 is arranged in the servo valve 5; the swash plate displacement LVDT sensor 7 is connected to the variable displacement plunger pump 2 through threads and bolts; the pressure sensor 8 is connected to the variable displacement plunger pump 2 by a screw thread.
The flow of the outlet of the variable plunger pump 2 is introduced into a port P of the servo valve 5 and enters the variable piston main cylinder 3 according to the displacement proportion of the valve core of the servo valve 5, and when the pressure of the rodless cavity of the variable piston main cylinder 3 is larger than the spring force of the variable piston auxiliary cylinder 4, the displacement of the variable plunger pump 2 is reduced; when the pressure of the rodless cavity of the piston main cylinder 3 is smaller than the spring force of the variable piston auxiliary cylinder 4, the displacement of the variable plunger pump 2 is increased.
The displacement of the variable plunger pump 2 is determined by the force balance of the variable piston main cylinder 3 and the variable piston secondary cylinder 4, and the pump displacement is reduced when the hydraulic thrust of the rod-free cavity of the variable piston main cylinder 3 is higher than the spring force of the variable piston secondary cylinder 4, otherwise, the displacement is increased. When the pump is in a shutdown state or the pressure of the pump outlet is lower, the oil in the rodless cavity of the variable piston main cylinder 3 enters the shell 11 through the valve cross position, the pressure of the rodless cavity is lower, the spring force of the variable piston auxiliary cylinder 4 pushes the pump displacement to be maximum, the maximum flow is output, after the high pressure is built at the pump outlet, the high-pressure oil in the pump outlet can enter the servo valve 5, the displacement and the change of the pump are controlled by the valve core position of the servo valve 5, and the displacement of the variable plunger pump 2 can be changed by changing the current of the servo valve 5.
The swash plate displacement LVDT sensor 7 comprises an LVDT sensor housing 31, an LVDT sensor inner core 32, an LVDT sensor protective shell 30 and an LVDT sensor connecting rod 26, one end of the LVDT sensor connecting rod 26 is connected with a piston of the variable piston master cylinder 3 through threads, the other end of the LVDT sensor connecting rod 26 is provided with the LVDT sensor inner core 32 in an interference fit mode, the LVDT sensor protective shell 30 is connected with a cylinder of the variable piston master cylinder 3 through a fixing bolt 28, the LVDT sensor protective shell 30 is connected with the LVDT sensor housing 31 through threads, and the LVDT sensor inner core 32 is located in the LVDT sensor housing 31.
The cylinder of the variable piston master cylinder 3 is sealed with the LVDT sensor connecting rod 26 through a Glare ring 27, and the Glare ring 27 seals oil in the variable piston master cylinder 3. And the cylinder barrel of the variable piston master cylinder 3 and the protective shell 30 of the LVDT sensor are sealed by a dustproof O-shaped ring 29.
The outer wall of the LVDT sensor housing 31 is in threaded connection with a locking nut 33, the locking nut 33 abuts against the end face of the LVDT sensor protective housing 30, and the locking nut 33 is used for fixing the position of the LVDT sensor housing 31. The signal of the swash plate displacement LVDT sensor 7 is led out through a connecting cable 34.
In the structural design, a cylinder barrel of a variable piston main cylinder 3 of a variable plunger pump 2 is designed into a screw connection form, so that the variable plunger pump can be conveniently connected with a pump; the LVDT sensor inner core 32 is fixed to the piston of the variable piston master cylinder 3 by the LVDT sensor connecting rod 26, and the LVDT sensor housing 31 is fixed to the cylinder of the variable piston master cylinder 3 by the LVDT sensor shield 30. When the cylinder barrel and the piston of the variable piston master cylinder 3 move relatively, the LVDT sensor shell 31 and the LVDT sensor inner core 32 are driven to move relatively, so that a piston displacement signal of the variable piston master cylinder 3 is generated and is led out by a connecting cable 34; the dust-proof O-ring 29 is used to prevent external dust and foreign substances from entering the variable piston master cylinder 3.
The pressure flow adaptive control of the present invention is implemented in the controller 9; the controller 9 comprises a first differential voltage amplifier 12.1, a second differential voltage amplifier 12.2, a third differential voltage amplifier 12.3, a first ramp signal generator 13.1, a second ramp signal generator 13.2, a divider 14, a first minimum value selector 15.1, a second minimum value selector 15.2, a first absolute value generator 16.1, a second absolute value generator 16.2, a pressure closed-loop controller 17, a flow closed-loop controller 18, a pressure flow adaptive selector 19, a spool displacement closed-loop controller 20, a current closed-loop controller 21, a first modem 22.1, a second modem 22.2, a first sensor signal regulator 23.1, a second sensor signal regulator 23.2, a third sensor signal regulator 23.3, a current-voltage converter 24 and a servo valve driver 25;
the pressure closed-loop module comprises a differential voltage amplifier I12.1, a ramp signal generator I13.1, a pressure closed-loop controller 17, a sensor signal regulator III 23.3 and a current-voltage converter 24. The pressure instruction Pc enters a pressure closed-loop controller 17 through the quantitative conversion of a differential voltage amplifier I12.1 and a ramp signal generator I13.1, the actual pressure Pa enters the pressure closed-loop controller 17 through the quantitative conversion of a current-voltage converter 24 and a sensor signal regulator III 23.3, and the pressure closed-loop controller 17 generates a pressure closed-loop value through proportional, integral and differential advanced calculation; the pressure instruction Pc and the actual pressure Pa are input values, and the pressure closed-loop value is an output module; the differential voltage amplifier I12.1 amplifies the pressure command Pc, the ramp signal generator I13.1 performs quantization conversion on the pressure command Pc, the current-voltage converter 24 performs voltage conversion on the actual pressure signal Pa, and the sensor signal regulator III 23.3 performs quantization conversion on the signal.
The power calculation module includes a second differential voltage amplifier 12.2, a divider 14, and a first minimum selector 15.1. The power is in direct proportion to the product of the pressure and the flow, so that the flow instruction value can be obtained by dividing the power instruction by the pressure feedback value, the flow instruction value is compared with the actual flow instruction, and a small value is selected, so that the output power of the pump is ensured to be not higher than the power instruction Wc; dividing the power command Wc by the actual pressure Pa quantized value through the quantized conversion of a second differential voltage amplifier 12.2, comparing the power command Wc with the displacement command Vc by the quantized conversion of a third differential voltage amplifier 12.3 and a second ramp signal generator 13.2 for minimum value, selecting a smaller value to enter the flow closed-loop controller 18, enabling the swash plate displacement Sa2 to enter the flow closed-loop controller 18 through the quantized conversion of a first modem 22.1 and a first sensor signal regulator 23.1, and enabling the flow closed-loop controller 18 to generate a flow closed-loop value through proportional, integral and differential calculation; firstly, the second differential voltage amplifier 12.2 quantizes the power command Wc, divides the quantized power command Wc by the quantized actual pressure Pa, and enters the first minimum value selector 15.1; the third differential voltage amplifier 12.3 amplifies the displacement instruction Vc, and the second ramp signal generator 13.2 performs quantization conversion on the displacement instruction Vc and enters the first minimum value selector 15.1; the minimum value selector one 15.1 selects the smaller value and enters the flow closed-loop controller 18.
The displacement closed-loop module comprises a third differential voltage amplifier 12.3, a second ramp signal generator 13.2, a displacement closed-loop controller 18, a first modem 22.1 and a first sensor signal regulator 23.1. The displacement instruction Vc and the swash plate displacement Sa2 are input values, and the flow closed-loop value is an output module; the third differential voltage amplifier 12.3 amplifies the displacement instruction Vc, and the second ramp signal generator 13.2 performs quantization conversion on the displacement instruction Vc and enters the flow closed-loop controller 18; the first modem 22.1 converts a swash plate displacement Sa2 signal from a pulse signal into an analog signal, and the first sensor signal regulator 23.1 performs quantitative conversion on the analog signal and enters the displacement closed-loop controller 18; the displacement closed-loop controller 18 performs proportional, differential look-ahead, and integral processing on the signal after the quantization conversion to generate a flow closed-loop value.
In a control system of a pump, only the position of a variable piston rod, namely the angle of a swash plate, can not control the pressure and the flow of the system at the same time, only one of the variable piston rod and the swash plate can be selected to control under different working conditions, but the definition of the different working conditions is a tedious matter. However, this situation can be avoided by the adaptive pressure-flow selector 19, which includes a second minimum selector 15.2, a first absolute value generator 16.1 and a second absolute value generator 16.2 in the adaptive pressure-flow selector 19. The pressure-flow adaptive selector 19 selects a closed-loop value whose absolute value is smaller as an output value. The controller 9 sets a pressure command Pc and a displacement command Vc, when the pump is started, the pump displacement rises to be close to Vc quickly, the pressure is not established at the outlet, at this time, the pressure flow adaptive selector 19 selects a smaller flow closed-loop value as an output value, when the oil is filled in the cavity, the pressure is established to be close to Pc, at this time, the pressure flow adaptive selector 19 selects a smaller flow closed-loop value as an output value, and the pump displacement returns to a position close to 0 to maintain the balance of the leakage amount.
The spool displacement closed-loop module comprises a spool displacement closed-loop controller 20, a second modem 22.2 and a second sensor signal regulator 23.2. The pressure closed-loop value and the flow closed-loop value select a closed-loop value meeting the requirement through a pressure flow adaptive selector 19 and enter a valve core displacement closed-loop controller 20, the valve core displacement Sa1 enters the valve core displacement closed-loop controller 20 through the quantitative conversion of a modem II 22.2 and a sensor signal regulator II 23.2, and the valve core displacement closed-loop controller 20 generates a voltage command value through proportional and differential preceding calculation; the second modem 22.2 converts the spool displacement Sa1 signal from a pulse signal into an analog signal, and the second sensor signal regulator 23.2 performs quantization conversion on the analog signal.
The current closed-loop module comprises a current closed-loop controller 21 and a servo valve driver 25. The voltage command value generated by the valve element displacement closed-loop controller 20 is converted from voltage to current through the servo valve driver 25, and enters the current closed-loop controller 21, the actual current Ia of the servo valve 5 enters the current closed-loop controller 21, and the current closed-loop controller 21 generates the command current Ic through proportional calculation.
The above embodiments are merely illustrative, and not restrictive, and various changes may be made by those skilled in the art without departing from the spirit and scope of the invention, and therefore all equivalent technical solutions are intended to fall within the scope of the invention.

Claims (7)

1. The utility model provides an intelligence aviation variable plunger pump pressure flow self-adaptation control system which characterized in that: the variable plunger pump comprises a motor (1), a variable plunger pump (2), a servo valve (5), a valve element displacement sensor (6) for detecting the valve element displacement of the servo valve (5), a swash plate displacement LVDT sensor (7), a pressure sensor (8) for detecting the outlet pressure of the variable plunger pump (2), a controller (9), a pressurizing oil tank (10) for supplying oil to the variable plunger pump (2) and a shell (11), wherein the variable plunger pump (2) is provided with a variable piston main cylinder (3) and a variable piston auxiliary cylinder (4), the output end of the motor (1) is connected with the variable plunger pump (2), oil drainage of the variable plunger pump (2) and oil at a T port of the servo valve (5) return to the shell (11), the variable piston main cylinder (3) is moved by the oil of the servo valve (5), and the swash plate displacement LVDT sensor (7) is used for detecting the displacement of the variable piston main cylinder (3), the controller (9) receives the spool displacement Sa1 of the spool displacement sensor (6), the swash plate displacement Sa2 of the swash plate displacement LVDT sensor (7), the actual pressure Pa of the pressure sensor (8), the actual current Ia of the servo valve (5), a pressure command Pc, a displacement command Vc and a power command Wc, and outputs a command current Ic to the electromagnet of the servo valve (5) through operation;
the controller (9) comprises a divider (14), a first minimum value selector (15.1), a second minimum value selector (15.2), a first absolute value generator (16.1), a second absolute value generator (16.2), a pressure closed-loop controller (17), a flow closed-loop controller (18), a pressure flow self-adaptive selector (19), a valve core displacement closed-loop controller (20) and a current closed-loop controller (21);
the quantized value of the pressure command Pc and the quantized value of the actual pressure Pa enter a pressure closed-loop controller (17), and the pressure closed-loop controller (17) generates a pressure closed-loop value through calculation;
dividing the quantized value of the power command Wc by the quantized value of the actual pressure Pa, performing minimum comparison with the quantized value of the displacement command Vc, selecting a smaller value to enter a flow closed-loop controller (18), entering the quantized value of the swash plate displacement Sa2 to enter the flow closed-loop controller (18), and generating a flow closed-loop value by the flow closed-loop controller (18) through calculation;
the pressure closed-loop value and the flow closed-loop value are selected to be in accordance with the requirement through a pressure flow self-adaptive selector (19) and enter a valve core displacement closed-loop controller (20), the quantized value of the valve core displacement Sa1 enters the valve core displacement closed-loop controller (20), and the valve core displacement closed-loop controller (20) generates a voltage instruction value through calculation;
the quantized value of the voltage instruction value enters a current closed-loop controller (21), the actual current Ia of the servo valve (5) enters the current closed-loop controller (21), and the current closed-loop controller (21) generates an instruction current Ic through calculation;
the pressure and flow adaptive selector (19) comprises a second minimum selector (15.2), a first absolute value generator (16.1) and a second absolute value generator (16.2), wherein the second minimum selector (15.2) selects a closed-loop value with a smaller absolute value in the first absolute value generator (16.1) and the second absolute value generator (16.2) as an output value;
the quantized value of the power command Wc divided by the quantized value of the actual pressure Pa is divided in a divider (14) to obtain a flow command value, and the minimum value comparison of the flow command value obtained in the divider (14) and the quantized value of the displacement command Vc is performed in a minimum value selector one (15.1).
2. The intelligent adaptive control system for the pressure flow of the aviation variable displacement plunger pump according to claim 1, characterized in that: the servo valve (5), the swash plate displacement LVDT sensor (7) and the pressure sensor (8) are all connected to the variable displacement plunger pump (2), and the spool displacement sensor (6) is installed in the servo valve (5).
3. The intelligent adaptive control system for the pressure and the flow of the aviation variable displacement plunger pump according to claim 1, wherein: the flow of the outlet of the variable plunger pump (2) is introduced into a P port of the servo valve (5) and enters the variable piston main cylinder (3) according to the displacement proportion of a valve core of the servo valve (5), and when the pressure of a rodless cavity of the variable piston main cylinder (3) is larger than the spring force of the variable piston auxiliary cylinder (4), the displacement of the variable plunger pump (2) is reduced; when the pressure of the rodless cavity of the piston main cylinder (3) is smaller than the spring force of the variable piston auxiliary cylinder (4), the displacement of the variable plunger pump (2) is increased.
4. The intelligent adaptive control system for the pressure and the flow of the aviation variable displacement plunger pump according to claim 1, wherein: the swash plate displacement LVDT sensor (7) comprises an LVDT sensor shell (31), an LVDT sensor inner core (32), an LVDT sensor protective shell (30) and an LVDT sensor connecting rod (26), one end of the LVDT sensor connecting rod (26) is connected to a piston of the variable piston master cylinder (3) in a threaded mode, the LVDT sensor inner core (32) is installed at the other end of the LVDT sensor connecting rod (26) in an interference fit mode, the LVDT sensor protective shell (30) is connected with a cylinder of the variable piston master cylinder (3) through a fixing bolt (28), the LVDT sensor protective shell (30) is connected with the LVDT sensor shell (31) through threads, and the LVDT sensor inner core (32) is located in the LVDT sensor shell (31).
5. The intelligent adaptive control system for aviation variable displacement plunger pump pressure and flow rate according to claim 4, wherein: the cylinder barrel of the variable piston master cylinder (3) is sealed with the LVDT sensor connecting rod (26) through a Glare ring (27), and the cylinder barrel of the variable piston master cylinder (3) is sealed with the LVDT sensor protective shell (30) through a dustproof O-shaped ring (29).
6. The intelligent adaptive control system for aviation variable displacement plunger pump pressure and flow rate according to claim 4, wherein: the outer wall of the LVDT sensor shell (31) is in threaded connection with a locking nut (33), the locking nut (33) abuts against the end face of the LVDT sensor protective shell (30), and signals of the swash plate displacement LVDT sensor (7) are led out through a connecting cable (34).
7. The intelligent adaptive control system for the pressure and the flow of the aviation variable displacement plunger pump according to claim 1, wherein: the controller (9) comprises a first differential voltage amplifier (12.1), a second differential voltage amplifier (12.2), a third differential voltage amplifier (12.3), a first ramp signal generator (13.1), a second ramp signal generator (13.2), a first modem (22.1), a second modem (22.2), a first sensor signal regulator (23.1), a second sensor signal regulator (23.2), a third sensor signal regulator (23.3), a current-voltage converter (24) and a servo valve driver (25);
the pressure instruction Pc enters a pressure closed-loop controller (17) through the quantitative conversion of a differential voltage amplifier I (12.1) and a ramp signal generator I (13.1), the actual pressure Pa enters the pressure closed-loop controller (17) through the quantitative conversion of a current-voltage converter (24) and a sensor signal regulator III (23.3), and the pressure closed-loop controller (17) generates a pressure closed-loop value through proportional, integral and differential advanced calculation;
dividing a power command Wc by a quantized value of an actual pressure Pa through quantized conversion of a differential voltage amplifier II (12.2), comparing the power command Wc with a displacement command Vc through the quantized conversion of a differential voltage amplifier III (12.3) and a ramp signal generator II (13.2) to carry out minimum value, selecting a smaller value to enter a flow closed-loop controller (18), enabling a swash plate displacement Sa2 to enter the flow closed-loop controller (18) through the quantized conversion of a modem I (22.1) and a sensor signal regulator I (23.1), and enabling the flow closed-loop controller (18) to generate a flow closed-loop value through proportional, integral and differential advanced calculation;
the pressure closed-loop value and the flow closed-loop value are selected to be in accordance with the requirement through a pressure flow self-adaptive selector (19) and enter a valve core displacement closed-loop controller (20), valve core displacement Sa1 enters the valve core displacement closed-loop controller (20) through quantitative conversion of a modem II (22.2) and a sensor signal regulator II (23.2), and the valve core displacement closed-loop controller (20) generates a voltage command value through proportional and differential preceding calculation;
the voltage instruction value is converted into a current value through a servo valve driver (25) and enters a current closed-loop controller (21), the actual current Ia of the servo valve (5) enters the current closed-loop controller (21), and the current closed-loop controller (21) generates an instruction current Ic through proportional calculation.
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