CN111102261B - Force feedback positive gain type electrohydraulic pressure servo valve - Google Patents
Force feedback positive gain type electrohydraulic pressure servo valve Download PDFInfo
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- CN111102261B CN111102261B CN201911346667.6A CN201911346667A CN111102261B CN 111102261 B CN111102261 B CN 111102261B CN 201911346667 A CN201911346667 A CN 201911346667A CN 111102261 B CN111102261 B CN 111102261B
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- valve core
- nozzle
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- pressure
- brake
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/028—Shuttle valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/021—Valves for interconnecting the fluid chambers of an actuator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
- F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K27/00—Construction of housing; Use of materials therefor
- F16K27/04—Construction of housing; Use of materials therefor of sliding valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0603—Multiple-way valves
- F16K31/061—Sliding valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0675—Electromagnet aspects, e.g. electric supply therefor
- F16K31/0679—Electromagnet aspects, e.g. electric supply therefor with more than one energising coil
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Electromagnetism (AREA)
- Magnetically Actuated Valves (AREA)
- Servomotors (AREA)
Abstract
The invention belongs to the field of hydraulic pressure, and particularly relates to a force feedback positive gain type electrohydraulic pressure servo valve. The servo valve is used for an electronic anti-skid brake system of an airplane and comprises: the hydraulic valve comprises a shell, a torque motor, a left nozzle, a right nozzle, a baffle, a feedback rod, a left orifice, a right orifice, a valve sleeve, a valve core left control cavity, a valve core right control cavity and an oil inlet, a brake port and an oil return port are arranged on the shell.
Description
Technical Field
The invention belongs to the field of hydraulic pressure, and particularly relates to a force feedback positive gain type electrohydraulic pressure servo valve.
Background
At present, most of electrohydraulic pressure servo valves used for domestic main machine types are pressure servo valves without force feedback, and a schematic diagram is shown in fig. 1. The valve of the structure type has no force feedback in the stroke of the pre-stage, is easy to whistle and shake under high pressure and high temperature, has no feedback rod force feedback in the second-stage slide valve, has short stroke of the valve core, low control precision and poor stability of the valve core.
Disclosure of Invention
The invention aims to: the force feedback positive gain type electrohydraulic pressure servo valve is mainly applied to receiving system instructions, switching on and off an oil supply circuit of a brake system, and controlling and outputting certain brake pressure, wherein the brake pressure is increased along with the increase of control current.
The invention provides a force feedback positive gain type electrohydraulic pressure servo valve, which is used for an electronic anti-skid brake system of an airplane, and comprises the following components: the second shell, the torque motor, the second left nozzle, the second right nozzle, the baffle, the feedback rod, the second left orifice, the right orifice, the valve sleeve, the second valve core, the left valve core control cavity, the right valve core control cavity and the second shell are provided with an oil inlet, a brake port and an oil return port;
the oil inlet, the second left throttle hole, the second left nozzle and the oil overflow cavity are communicated with the oil return port through a left oil way; the oil inlet, the right orifice, the second right nozzle, the oil overflow cavity and the oil return port are communicated through a right oil way; the two sides of the baffle of the torque motor are provided with a second left nozzle and a second right nozzle; hydraulic oil ejected from the second left nozzle and the second right nozzle flows into the overflow cavity through the baffle plate;
the second valve core is arranged in the valve sleeve and can axially move in the valve sleeve, and the valve sleeve is fixed in the second shell; the lower end of the second valve core is provided with a brake cavity; the brake cavity is communicated with the brake port; the second valve core is provided with a pressure feedback channel; the pressure feedback channel communicates the brake port with the right control cavity of the valve core;
the cavities at two ends of the second valve core in the valve sleeve are left valve core control cavities and right valve core control cavities; an inlet of the second left nozzle and a left control cavity of the valve core; an inlet of the second right nozzle and a valve core right control cavity; one end of the feedback rod is fixed at the lower end of the baffle plate, and the other end of the feedback rod penetrates through the valve sleeve and is inserted into the annular groove on the second valve core.
The oil in the oil inlet enters the left nozzle and the right nozzle through the oil filter and the left orifice and the right orifice, and is shot on the baffle plate to generate feedback pressure and enter the oil return cavity.
When the armature component of the torque motor is in the zero position, gaps between the baffle and the left nozzle and the right nozzle are equal, and the flow rate of the left nozzle and the right nozzle passing through the gaps is the same.
When the armature assembly of the torque motor rotates, the gap between the baffle and the left nozzle and the gap between the baffle and the right nozzle are unequal, and the flow of the left nozzle and the right nozzle through the gap is changed.
When the second valve core moves rightwards, the second valve core gradually opens the window between the brake cavity and the oil inlet, and gradually closes the windows of the brake cavity and the oil return port.
Under the condition that the second valve core does not move initially, the brake cavity is communicated with the oil return port, and the brake cavity is not communicated with the oil inlet.
The second left nozzle and the second right nozzle are opposite to each other.
The other end of the feedback rod is provided with a feedback rod ball inserted into the annular groove.
The invention has the beneficial effects that: the structure greatly optimizes the electrohydraulic pressure servo valve, and greatly enhances the stability and reliability of the valve through the optimization of two-stage force feedback of the spray gear valve core. The valve can work stably for a long time, and is suitable for mass production.
Drawings
FIG. 1 is a schematic diagram of a force-less feedback type electrohydraulic pressure servo valve.
The device comprises a 16-upper magnetizer, a 17-lower magnetizer, a 18-baffle, a 19-first right nozzle, a 20-right orifice, a 21-right floating sleeve, a 22-right limiting block, a 23-first shell, a 24-spring, a 25-first valve core, a 26-oil filter, a 27-left limiting block, a 28-left floating sleeve, a 29-first left orifice, a 30-first left nozzle, a 31-first spring tube, a 32-first armature, a 33-first left coil and a 35-first right coil.
FIG. 2 is a schematic diagram of a force feedback positive gain pressure servo valve.
Wherein, the liquid crystal display device comprises a liquid crystal display device, 1-second left coil, 2-second right coil, 3-second right nozzle, 4-first baffle, 5-feedback rod, 6-right orifice, 7-feedback rod ball, 8-valve pocket, 9-valve core right control chamber, 10-second valve core, 11-valve core left control chamber, 12-second left orifice, 13-second left nozzle, 14-second shell, 15-moment motor.
Fig. 3 is a schematic view of a feedback rod.
Wherein 34-second armature, 36-second baffle, 37-armature assembly screw, 38-second spring tube.
Fig. 4 is a block diagram of a positive gain spool valve design.
The valve comprises a 10-second valve core, an 8-valve sleeve, a 39-limiting block, a 14-second shell, a 40-pressure feedback hole, a P-oil cavity, an S-brake cavity and an R-oil return cavity.
Detailed Description
The invention provides a force feedback positive gain type electrohydraulic pressure servo valve, which is shown in figure 2 and is mainly used for an electronic anti-skid brake system of an airplane. The basic functions are as follows: and receiving a system instruction, switching on and off an oil supply circuit of the brake system, and controlling and outputting a certain brake pressure which is increased along with the increase of the control current.
As shown in fig. 2-4, when any one coil of the servo valve obtains a forward control current, a control moment is generated on the second armature due to the interaction of the control magnetic flux and the polarized magnetic flux, so that the armature assembly deflects clockwise around the pivot of the second spring tube, the baffle plate deflects leftwards, the second left nozzle baffle plate interval is reduced to increase the pressure of the left control cavity, the second right nozzle baffle plate interval is increased to decrease the pressure of the right control cavity, the two control cavities generate a pressure difference (left high and right low) to act on the left control end face and the right control end face of the second valve core, when the pressure difference is enough to overcome the spring force of the feedback rod, the second valve core moves rightwards, the oil return window area is continuously reduced, the brake oil inlet window area is continuously increased, the output brake pressure is increased, and when the pressure difference at the two ends of the second valve core and the feedback force of the feedback rod are balanced, the second valve core stops moving, and the pressure valve outputs stable brake pressure. So that the brake pressure output by the valve is in one-to-one proportional correspondence with the input current value: the larger the input current is, the larger the output brake pressure is, so that the pressure control of positive gain is realized, and the pressure control of the positive gain of the servo valve is also realized.
In contrast, when the coil obtains a negative control current, the baffle deflects rightwards, the pressure difference (right high left low) of the nozzle cavity enables the second valve core to be more firmly propped against the left limiting block than the original state, the state that the brake oil inlet window is completely closed and the oil return window is completely opened is always kept, and the pressure output to the brake cavity is constantly equal to the oil return pressure.
Claims (1)
1. A force feedback positive gain type electrohydraulic pressure servo valve for an aircraft electronic anti-skid brake system, comprising: the second left coil (1), the second right coil (2), the second shell (14), the torque motor (15), the second left nozzle (13), the second right nozzle (3), the first baffle (4), the feedback rod (5), the second left orifice (12), the right orifice (6), the valve sleeve (8), the second valve core (10), the valve core left control cavity (11), the valve core right control cavity (9) and the second shell (14) are provided with an oil inlet, a brake port and an oil return port;
the oil inlet, the second left throttle hole (12), the second left nozzle (13) and the oil overflow cavity are communicated with the oil return port through a left oil way; the oil inlet, the right orifice (6), the second right nozzle (3) and the oil overflow cavity are communicated with the oil return port through a right oil way; two sides of a baffle of the torque motor are provided with a second left nozzle (13) and a second right nozzle (3); hydraulic oil ejected from the second left nozzle (13) and the second right nozzle (3) flows into the overflow cavity through the first baffle (4);
the second left throttle hole (12) and the right throttle hole (6) are arranged on the same side of the feedback rod (5);
the second valve core (10) is arranged in the valve sleeve (8) and can axially move in the valve sleeve (8), and the valve sleeve (8) is fixed in the second shell (14); the lower end of the second valve core (10) is provided with a brake cavity; the brake cavity (S) is communicated with the brake port; the second valve core (10) is provided with a pressure feedback channel; the pressure feedback channel communicates the brake port with the right control cavity (9) of the valve core;
cavities at two ends of a second valve core (10) in the valve sleeve (8) are a left valve core control cavity (11) and a right valve core control cavity (9); an inlet of the second left nozzle (13) is communicated with the valve core left control cavity (11); the inlet of the second right nozzle (3) is communicated with a valve core right control cavity (9); one end of the feedback rod (5) is fixed at the lower end of the second baffle plate (36), and the other end of the feedback rod penetrates through the valve sleeve (8) and is inserted into a ring groove on the second valve core (10);
when any coil of the servo valve obtains forward control current, a control moment is generated on the second armature (34) due to interaction of control magnetic flux and polarized magnetic flux, a holding assembly screw (37) deflects clockwise around a fulcrum of a second spring tube (38), the first baffle (4) deflects leftwards, the distance between the second left nozzle (13) and the first baffle (4) is reduced, the pressure of a left control cavity (11) of a valve core is increased, the distance between the second right nozzle (3) and the first baffle (4) is increased, the pressure of a right control cavity (9) of the valve core is reduced, the two control cavities generate pressure differences, the pressure differences act on left and right control end surfaces of the second valve core (10), when the pressure differences are enough to overcome the spring force of a feedback rod (5), the second valve core (10) moves rightwards, the area of an oil return window is continuously reduced, the area of a brake oil inlet window is continuously increased, the output brake pressure is increased, and when the pressure difference between two ends of the second valve core (10) and the feedback force of the feedback rod (5) are balanced, the movement of the second valve core (10) stops, and the brake pressure valve is stable;
when the coil obtains a negative control current, the first baffle (4) deflects rightwards, the pressure difference of the nozzle cavity enables the second valve core (10) to be more firmly propped against the left limiting block than the original state, the state that the brake oil inlet window is completely closed and the oil return window is completely opened is always kept, and the pressure output to the brake cavity is always equal to the oil return pressure;
oil in the oil inlet enters the left nozzle and the right nozzle through the oil filter and the left orifice and the right orifice, and is shot on the baffle plate to generate feedback pressure and enter the oil return cavity;
when the armature component of the torque motor is at the zero position, gaps between the baffle and the left nozzle and the right nozzle are equal, and the flow rate of the left nozzle and the right nozzle passing through the gaps is the same;
when the armature component of the torque motor rotates, the gap between the baffle and the left nozzle and the gap between the baffle and the right nozzle are unequal, and the flow of the left nozzle and the right nozzle through the gap is changed;
when the second valve core (10) moves rightwards, the second valve core (10) gradually opens a window between the brake cavity and the oil inlet, and gradually closes windows of the brake cavity and the oil return port;
under the condition that the second valve core (10) does not move initially, the brake cavity is communicated with the oil return port, and the brake cavity is not communicated with the oil inlet;
the second left nozzle and the second right nozzle are opposite;
the other end of the feedback rod is provided with a feedback rod ball inserted into the annular groove;
the force feedback positive gain type electrohydraulic pressure servo valve is used for receiving the instruction of the electronic anti-skid braking system of the airplane, switching on and off an oil supply circuit of the braking system, controlling and outputting a certain braking pressure, and increasing the braking pressure along with the increase of control current.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911346667.6A CN111102261B (en) | 2019-12-24 | 2019-12-24 | Force feedback positive gain type electrohydraulic pressure servo valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911346667.6A CN111102261B (en) | 2019-12-24 | 2019-12-24 | Force feedback positive gain type electrohydraulic pressure servo valve |
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| Publication Number | Publication Date |
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| CN111102261A CN111102261A (en) | 2020-05-05 |
| CN111102261B true CN111102261B (en) | 2023-04-21 |
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| CN201911346667.6A Active CN111102261B (en) | 2019-12-24 | 2019-12-24 | Force feedback positive gain type electrohydraulic pressure servo valve |
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Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2713192Y (en) * | 2004-07-22 | 2005-07-27 | 上海航天控制工程研究所 | Micro flow force feedback electro-hydraulic servo valve |
| CN102094865B (en) * | 2009-12-11 | 2013-05-08 | 陈镇汉 | Intelligent electrohydraulic flow servo valve |
| CN201851415U (en) * | 2010-11-09 | 2011-06-01 | 韩晓新 | Electro-hydraulic servo valve |
| FR3005133B1 (en) * | 2013-04-26 | 2015-11-20 | In Lhc | SERVOVALVE PRESSURE WITH REDUCED NOISE. |
| CN204226322U (en) * | 2014-11-11 | 2015-03-25 | 九江中船仪表有限责任公司（四四一厂） | A kind of electrohydraulic control |
| CN204436910U (en) * | 2014-12-09 | 2015-07-01 | 上海朝田实业有限公司 | A kind of asymmetric hydraulic efficiency servo-valve |
| CN105570225A (en) * | 2016-03-03 | 2016-05-11 | 安徽万荣航天设备有限公司 | Ultra-low-pressure large-flow electro-hydraulic servo valve |
| CN109760825A (en) * | 2019-01-30 | 2019-05-17 | 西安航空制动科技有限公司 | A kind of steerable electrohydraulic servo valve |
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2019
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| CN111102261A (en) | 2020-05-05 |
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