CN109760826B - Electrohydraulic servo valve capable of being operated by liquid transmission - Google Patents
Electrohydraulic servo valve capable of being operated by liquid transmission Download PDFInfo
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- CN109760826B CN109760826B CN201910088985.0A CN201910088985A CN109760826B CN 109760826 B CN109760826 B CN 109760826B CN 201910088985 A CN201910088985 A CN 201910088985A CN 109760826 B CN109760826 B CN 109760826B
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Abstract
An electrohydraulic servo valve capable of being operated by liquid transmission, a shell, a torque motor, a pre-stage and a slide valve stage. The torque motor is mounted on the housing. The pre-stage and the slide valve stage are both assembled in the housing and are hydraulically connected to each other. Two ends of a spool valve core in the spool valve stage are respectively communicated with the brake port and the oil return port; the shell is provided with a hydraulic control cavity communicated with the spool cavity of the spool valve, and the central line of the hydraulic control cavity is coaxial with the central line of the spool cavity of the spool valve. The hydraulic control cavity is positioned on the shell at one side of the oil return port. The hydraulic control port on the shell is communicated with the hydraulic control cavity and is connected with the hydraulic control pipeline of the airplane. The hydraulic brake pressure control system outputs required hydraulic brake pressure through hydraulic transmission control, and has important practical significance for the use of an electro-hydraulic servo valve for electric brake of an airplane, the popularization and application of an electric brake system of the airplane and the reliable and safe operation of the electric brake system of the airplane.
Description
Technical Field
The invention relates to an electro-hydraulic servo control technology of an airplane, in particular to an electro-hydraulic servo valve capable of controlling braking through liquid transmission, which is used for an electric brake system of the airplane.
Background
The electrohydraulic servo valve is a main accessory of an electric brake system of an airplane and bears the dual functions of a hydraulic brake valve and an anti-skid control valve. Such electrohydraulic servo valves are typically two-stage pressure positive gain type, and their construction includes a torque motor, a pre-stage, and a spool stage. The pre-stage is commonly used as a spray valve and also is a jet pipe valve. The pressure output characteristic of the positive gain electrohydraulic servo valve, namely the brake pressure, is in linear proportional relation with the control current. The hydraulic pressure required by the output of the slide valve stage of the electro-hydraulic servo valve can be controlled to be led to the braking machine wheel for braking by controlling the magnitude of the current input to the torque motor coil of the electro-hydraulic servo valve. From the composition and principle, the output of electrohydraulic servo valves is controlled and manipulated entirely by electrical signals (currents). Electro-hydraulic servo valves are not capable of being actuated and operated at all without manipulation of an electrical signal. In terms of hydraulic pressure, if a pre-stage fails, such as a spray gate valve or a jet pipe valve fails, the spool valve stage will not function properly, and the electro-hydraulic servo valve will not function properly as such. Thus, the electro-hydraulic servo valve for the conventional aircraft electric brake has the defect that no other externally operable means exist in the case of failure of the electric control or the electro-hydraulic control. This negatively affects aircraft electric brake applications. In practice, failure of the brake command sensor or failure of the anti-skid brake control box does not output, which can cause occurrence of an event that the electro-hydraulic servo valve cannot timely output brake pressure to brake the wheel due to no control current signal when a driver brakes. Hydraulic pre-stage faults also occur, so that the electro-hydraulic servo valve faults cause the landing running and braking accident symptoms of the aircraft. Thus, there is a need for a means other than electrical control that can operate electrohydraulic servo valve brakes in the event of a failure of the electrohydraulic control. In addition, in the aspect of take-off line braking, the reliability and applicability of the existing electrohydraulic servo valve are poor, the sporadic braking pressure cannot reach the maximum value, or an instantaneous pressure drop phenomenon occurs, and no alternative non-electric control other controllable means exists, so that the electrohydraulic servo valve can ensure the braking pressure required by constant output. In summary, the existing electrohydraulic servo valves for electric brakes of aircraft have the disadvantage of lacking other non-electronically controlled means for operating the spool valve stage thereof to normally and reliably output the required brake pressure when the electrohydraulic control fails, or when the output brake pressure cannot be used to meet the requirement of manual intervention, and the inherent disadvantage has a non-negligible effect on the application of the electric brake system of the aircraft and the reliable and safe operation of the electric brake system of the aircraft, so that improvement is needed to provide a means for operating in addition to the electric control.
The invention of 201310075475.2 provides an aircraft brake control valve, which relates to an improved electrohydraulic servo control valve for an aircraft electric brake system, is manufactured according to a modularized design, can provide inlet pressure and outlet pressure signals, and has the characteristics of good working stability, reliability and the like. This application also suffers from the disadvantage of having no externally manipulable means other than electrical control.
Disclosure of Invention
In order to overcome the defect that the prior art does not have other external controllable means from the electrical control, the invention provides an electrohydraulic servo valve capable of being controlled by liquid transmission.
The invention comprises the following steps: a housing, a torque motor, a pre-stage, and a spool stage. The torque motor is mounted on the housing using prior art techniques. The pre-stage and the slide valve stage are both assembled in the housing and are hydraulically connected to each other. The slide valve stage comprises a slide valve core and a slide valve sleeve; two ends of the spool valve are respectively communicated with the brake port and the oil return port; the hydraulic control device is characterized in that a hydraulic control cavity communicated with the spool valve cavity is formed in the shell, and the central line of the hydraulic control cavity is coaxial with the central line of the spool valve cavity. The hydraulic control cavity is positioned on the shell at one side of the oil return port. The shell is also provided with a hydraulic control port which is communicated with the hydraulic control cavity and is connected with an airplane hydraulic control pipeline.
The spool valve stage includes a spool valve spool and a valve sleeve. One end of the spool valve core of the spool valve is communicated with the hydraulic control port, and the other end of the spool valve core of the spool valve is communicated with the oil return port. Two radially protruding shoulders, a first shoulder and a second shoulder, are respectively arranged on the outer circumferential surface of the spool valve core. The first shoulder is used for controlling the oil return port; the outer end surface of the first shoulder, namely an annular band defined by the outer diameter of the shoulder and the outer diameter of the valve rod is a first control large end surface, and a control pressure from a pre-stage acts on the first control large end surface; the end face of the spool valve core at one end of the first shoulder is a small end face of the spool valve core; the pressure from the oil return port acts on the small end face of the spool valve. The second shoulder controls the pressure supply port; the outer end face of the second shoulder, i.e. the annular band defined by the outer diameter of the shoulder and the outer diameter of the valve stem, is a second large control end face on which the other control pressure from the pre-stage acts. The end face of the spool valve core at one end of the second shoulder is also a small end face of the spool valve core; pressure from the brake port acts on the small end face of the spool valve.
The shell is distributed and connected with a pressure source pipeline of an aircraft brake system, a brake port is connected with a pipeline of an aircraft brake wheel brake device, and an oil return port is connected with an aircraft oil return pipeline.
The torque motor is mechanically connected with the pre-stage, and the pre-stage is hydraulically connected with the slide valve stage. The pre-stage is communicated with the pressure supply port through an oil way in the shell, and a hydraulic oil filter and a fixed restriction orifice are arranged on the oil way leading to the pre-stage. Two large end surfaces of a spool valve core in the spool valve stage are communicated with the front stage through an oil way in the shell; one end of the spool valve core is communicated with the brake port, a spring is arranged on the large end face or the small end face of the spool valve core, and the other end of the spool valve core is communicated with the oil return port.
When the electrohydraulic servo valve is not electrified, the pressure supply port is closed, the oil return port is opened, the brake port is communicated with the oil return port, and the slide valve stage does not have hydraulic output; after the power is on, the torque motor operates the pre-stage to generate pressure change, the spool valve core of the spool valve generates displacement under the action of the pressure difference of the pre-stage, the first shoulder of the spool valve core of the spool valve is firstly enabled to close the oil return port, the second shoulder of the spool valve core of the spool valve is enabled to open the pressure supply port to feed oil, the pressure supply port is enabled to be communicated with the brake port, and the hydraulic pressure proportional to the control current is output.
The hydraulic control cavity is communicated with the hydraulic control port, the hydraulic control pressure from the hydraulic control port is led to and acts on the end face of the valve rod of the spool valve level, the spool valve of the spool valve level is directly pushed to displace hydraulically through the hydraulic control pressure from the hydraulic control port, and the spool valve level is controlled to output hydraulic pressure.
When the hydraulic control port of the hydraulic control cavity receives hydraulic pressure, the spool valve core is pushed to move under the action of the hydraulic pressure, and the first shoulder of the spool valve core closes the oil return port; further displacement, the second shoulder of the spool valve core of the spool valve level opens the pressure supply port to feed oil, so that the pressure supply port is communicated with the brake port, and the brake port outputs the required hydraulic pressure to brake; the larger the opening degree of the pressure supply port is, the larger the output brake pressure is;
when axial hydraulic thrust on the spool valve core is relieved, the spool valve core returns to an initial position under the action of hydraulic pressure and a spring, so that the pressure supply port is closed, the oil return port is opened, and the brake port is communicated with the oil return port.
The invention is operated by hydraulic transmission to output the required hydraulic brake pressure.
The invention is provided with a hydraulic control cavity of liquid transmission at one end of a slide valve of an electrohydraulic servo valve, and the hydraulic control cavity is used as an external controllable means to control the brake pressure required by the slide valve output of the slide valve by adopting liquid transmission when needed.
The hydraulic control cavity is arranged at the slide valve stage of the electrohydraulic servo valve, and hydraulic transmission is used as an external controllable means to control the slide valve stage to output the required brake pressure when needed. Under normal conditions, the hydraulic pressure output of the electrohydraulic servo valve is controlled by an electrical signal, namely, the pre-stage is controlled by a control current input to a torque motor coil, and then the pre-stage controls the slide valve stage to output hydraulic brake pressure in direct proportion to the magnitude of the control current. When the electrical signal control is lost, or the hydraulic pressure is not output by the spool valve stage due to the failure of the pre-stage, or the output of the spool valve stage is controlled by the electrohydraulic control and cannot meet the requirement of the maximum brake pressure required by stable output, such as the aircraft sliding during the take-off line braking, the maximum brake pressure is insufficient, and as long as a driver operates the brake sensor to input the hydraulic control pressure to the hydraulic control port, the hydraulic control pressure directly controls the brake pressure required by the spool valve stage output. Compared with an externally controllable means that the electro-hydraulic servo valve of the electric brake of the aircraft is only controlled by the inside of the control box, the control method of the electro-hydraulic servo valve of the electric brake of the aircraft is independent of electric signal control, the output of a slide valve stage can be manually controlled according to the requirement, the electro-hydraulic servo valve has a failure safety function, the usability of the electro-hydraulic servo valve is improved, the viability of an electro-hydraulic brake system of the aircraft is enhanced, and the reliable and safe operation of the electro-hydraulic brake system of the aircraft is ensured.
The electro-hydraulic servo valve is reasonable in structure, simple and practical, well overcomes the defect that the electro-hydraulic servo valve in the prior art is separated from electric control and has no other externally controllable means, and has important practical significance for the use of the electro-hydraulic servo valve for electric braking of an aircraft, the popularization and application of an electric braking system of the aircraft and the reliable and safe operation of the electric braking system of the aircraft.
Drawings
Fig. 1 is a schematic structural view of the present invention.
In the figure: 1. a housing; 2. a torque motor; 3. a pre-stage; 4. a slide valve stage; 5. a pressure supply port; 6. a brake port; 7. an oil return port; 8. oil filtering; 9. a fixed orifice; 10. a hydraulic control port; 11. a hydraulic control chamber.
Detailed Description
The embodiment is an electrohydraulic servo valve capable of being operated by liquid transmission, comprising: a housing 1, a torque motor 2, a pre-stage 3 and a slide valve stage 4. The torque motor 2 is mounted on the housing 1 using prior art techniques. The pre-stage 3 and the slide valve stage 4 are both fitted in the housing 1 and are hydraulically connected to each other between the pre-stage 3 and the slide valve stage. The pre-stage 3 and the slide valve stage 4 are both in the prior art.
The shell 1 is provided with a pressure supply port 5, a brake port 6 and an oil return port 7, wherein the pressure supply port is connected with a pressure supply source pipeline of an aircraft brake system, the brake port is connected with a brake device pipeline of an aircraft brake wheel, and the oil return port is connected with an aircraft oil return pipeline.
The torque motor 2 is mechanically connected to the pre-stage 3, and the pre-stage 3 is hydraulically connected to the slide valve stage 4. The pre-stage 3 communicates with the pressure supply port through an oil passage in the housing 1, and a hydraulic oil filter 8 and a fixed restriction 9 are provided on the oil passage leading to the pre-stage 3. Two large end surfaces of a spool valve core in the spool valve stage 4 are communicated with the pre-stage 3 through an oil way in the shell 1; one end of the spool valve core is communicated with the brake port, a spring is arranged on the large end face or the small end face of the spool valve core, and the other end of the spool valve core is communicated with the oil return port.
The housing is provided with a hydraulic control chamber 11 penetrating the spool chamber, and the center line of the hydraulic control chamber is coaxial with the center line of the spool chamber. The hydraulic control chamber is arranged on the shell at one side of the oil return opening 7. A hydraulic control port 10 is also formed in the housing and is communicated with the hydraulic control cavity. The hydraulic control port is connected with an airplane hydraulic control pipeline. In this embodiment, the hydraulic control chamber is a stepped hole.
The slide valve stage adopts the prior art and comprises a slide valve core and a valve sleeve. One end of the spool valve core of the spool valve is communicated with the hydraulic control port, and the other end of the spool valve core of the spool valve is communicated with the oil return port 7. In order to realize the communication between the two ends of the spool valve core and the hydraulic control port and the oil return port, two radial convex shoulders are arranged on the outer circumferential surface of the spool valve core, namely a first shoulder and a second shoulder. The first shoulder is used for controlling the oil return port; the outer end surface of the first shoulder, namely an annular band defined by the outer diameter of the shoulder and the outer diameter of the valve rod is a first control large end surface, and a control pressure from a pre-stage acts on the first control large end surface; the end face of the spool valve core at one end of the first shoulder is a small end face of the spool valve core; the pressure from the oil return port acts on the small end face of the spool valve. The second shoulder controls the pressure supply port; the outer end face of the second shoulder, i.e. the annular band defined by the outer diameter of the shoulder and the outer diameter of the valve stem, is a second large control end face on which the other control pressure from the pre-stage acts. The end face of the spool valve core at one end of the second shoulder is also a small end face of the spool valve core; pressure from the brake port acts on the small end face of the spool valve.
The torque motor 2, the pre-stage 3 and the slide valve stage 4, as well as the oil filter 8 and the fixed orifice 9 are all of the prior art. A spring is arranged at one end of the valve core according to the prior mode.
The pre-stage 3 of the embodiment is a double-nozzle baffle valve; the torque motor 2 is controllably and mechanically connected with a baffle plate of the double-nozzle baffle valve; the pressure oil at the pressure supply port is divided into two paths through an oil filter 8 and a fixed orifice 9, one path enters a nozzle, the other path enters a cavity where two large end surfaces of a spool of the spool valve stage 4 are located, and the pressure of the nozzle cavity of the nozzle baffle valve is communicated with the cavity where the large end surfaces of the spool valve stage 4 are located; a spring is arranged on the small end face of one end of the valve core communicated with the brake port; one end of the valve core is communicated with the brake port through an oil way in the valve core; the other end of the valve core is communicated with the oil return port through an oil way in the shell.
When the electrohydraulic servo valve is not electrified, the pressure supply port is closed, the oil return port is opened, the brake port is communicated with the oil return port, and the slide valve stage 4 does not have hydraulic output; after the power is on, the torque motor 2 operates the pre-stage 3 to generate pressure change, the spool valve core of the spool valve generates displacement under the effect of the pre-stage pressure difference, the first shoulder of the spool valve core of the spool valve is firstly enabled to close the oil return port, the second shoulder of the spool valve core of the spool valve is enabled to open the pressure supply port for oil inlet through further displacement, the pressure supply port is enabled to be communicated with the brake port, and the hydraulic pressure proportional to the control current is output.
The hydraulic control cavity 11 is communicated with the hydraulic control port 10, the hydraulic control pressure from the hydraulic control port 10 is led to and acts on the end face of the valve rod of the slide valve core of the slide valve stage 4, the slide valve core of the slide valve stage 4 is directly hydraulically pushed to displace by the hydraulic control pressure from the hydraulic control port 10, and the slide valve stage 4 is controlled to output hydraulic pressure.
The pilot port 10 is coupled to the hydraulic control lines of the aircraft, in particular to a hydraulic brake system, which in this embodiment is connected to a brake sensor operated by the driver, which is known in the art.
When a driver operates the brake sensor, the brake sensor outputs hydraulic pressure, the hydraulic pressure enters the hydraulic control port 10 through a pipeline, and the valve rod end face of the valve core of the slide valve grade 4 slide valve pushes the valve core of the slide valve grade 4 slide valve to move under the action of hydraulic pressure, and the first shoulder of the valve core of the slide valve grade 4 slide valve closes the oil return port. With further displacement of the spool valve core, the second shoulder of the spool valve core opens the pressure supply port to feed oil, so that the pressure supply port is communicated with the brake port, and the brake port outputs the required hydraulic pressure to brake; the larger the opening degree of the pressure supply port is, the larger the output brake pressure is.
The driver releases the operation of the brake sensor, the brake sensor releases the output hydraulic pressure, the axial hydraulic thrust on the spool of the spool valve stage 4 is released, the other end returns to the initial position under the action of the hydraulic pressure and the spring, the pressure supply port is closed, the oil return port is opened, and the brake port is communicated with the oil return port.
Claims (4)
1. A hydraulically operable electro-hydraulic servo valve comprising: a housing, a torque motor, a pre-stage and a slide valve stage; the torque motor is arranged on the shell by adopting the prior art; the pre-stage and the slide valve stage are both assembled in the shell, and the pre-stage and the slide valve stage are hydraulically connected; the slide valve stage comprises a slide valve core and a slide valve sleeve; two ends of the spool of the slide valve are respectively communicated with the brake port and the oil return port; the hydraulic control device is characterized in that a hydraulic control cavity communicated with a spool valve cavity is formed in the shell, and the central line of the hydraulic control cavity is coaxial with the central line of the spool valve cavity; the hydraulic control cavity is positioned on the shell at one side of the oil return port; the shell is also provided with a hydraulic control port which is communicated with the hydraulic control cavity and is connected with an airplane hydraulic control pipeline; the shell is also provided with a pressure supply port which is connected with a pressure supply source pipeline of the aircraft brake system, the brake port is connected with a brake device pipeline of the aircraft brake wheel, and the oil return port is connected with an aircraft oil return pipeline;
the slide valve stage comprises a slide valve core and a valve sleeve; the two ends of the spool valve core are respectively provided with a valve rod, one end of the spool valve core is communicated with the hydraulic control port, and the other end of the spool valve core is communicated with the oil return port; two radial convex shoulders are arranged on the outer circumferential surface of the spool valve core, namely a first shoulder and a second shoulder; the first shoulder is used for controlling the oil return port; the outer end surface of the first shoulder, namely an annular band defined by the outer diameter of the shoulder and the outer diameter of the valve rod, is a first control large end surface on which a control pressure from the pre-stage acts; the end face of the spool valve core at one end of the first shoulder is a small end face of the spool valve core; the pressure from the oil return port acts on the small end face of the spool of the slide valve; the second shoulder controls the pressure supply port; the outer end surface of the second shoulder, namely an annular band defined by the outer diameter of the shoulder and the outer diameter of the valve rod is a second large control end surface on which the other control pressure from the pre-stage acts; the end face of the spool valve core at one end of the second shoulder is also a small end face of the spool valve core; pressure from the brake port acts on the small end face of the spool valve.
2. The hydraulically operated electro-hydraulic servo valve of claim 1, wherein the torque motor is mechanically coupled to the pre-stage and the pre-stage is hydraulically coupled to the spool stage; the pre-stage is communicated with the pressure supply port through an oil way in the shell, and a hydraulic oil filter and a fixed restriction orifice are arranged on the oil way leading to the pre-stage; two large end surfaces of a spool valve core in the spool valve stage are communicated with the front stage through an oil way in the shell; one end of the spool valve core is communicated with the brake port, a spring is arranged on the large end face or the small end face of the spool valve core, and the other end of the spool valve core is communicated with the oil return port.
3. The hydraulically operated electro-hydraulic servo valve of claim 1, wherein the electro-hydraulic servo valve is controlled by the electro-hydraulic control, when not energized, the pressure supply port is closed, the oil return port is opened, the brake port is communicated with the oil return port, and the slide valve stage has no hydraulic output; after the power is on, the torque motor operates the pre-stage to generate pressure change, the spool valve core of the spool valve generates displacement under the action of the pressure difference of the pre-stage, the first shoulder of the spool valve core of the spool valve is firstly enabled to close the oil return port, the second shoulder of the spool valve core of the spool valve is enabled to open the pressure supply port to feed oil, the pressure supply port is enabled to be communicated with the brake port, and the hydraulic pressure proportional to the control current is output;
the hydraulic control cavity is communicated with the hydraulic control port, the hydraulic control pressure from the hydraulic control port is led to and acts on the end face of the valve rod of the spool valve level, the end face of the valve rod is the end face close to the hydraulic control cavity, the spool valve of the spool valve level is directly pushed to displace hydraulically by the hydraulic control pressure from the hydraulic control port, and the spool valve level is controlled to output hydraulic pressure.
4. The hydraulically operated electro-hydraulic servo valve as recited in claim 1, wherein when the pilot port of said pilot chamber receives hydraulic pressure, under the influence of the hydraulic pressure, the spool valve is urged to move, the first shoulder of the spool valve closing the return port; further displacement, the second shoulder of the spool valve core of the spool valve level opens the pressure supply port to feed oil, so that the pressure supply port is communicated with the brake port, and the brake port outputs the required hydraulic pressure to brake; the larger the opening degree of the pressure supply port is, the larger the output brake pressure is;
when axial hydraulic thrust on the spool valve core is relieved, the spool valve core returns to an initial position under the action of hydraulic pressure and a spring, so that the pressure supply port is closed, the oil return port is opened, and the brake port is communicated with the oil return port.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910088985.0A CN109760826B (en) | 2019-01-30 | 2019-01-30 | Electrohydraulic servo valve capable of being operated by liquid transmission |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910088985.0A CN109760826B (en) | 2019-01-30 | 2019-01-30 | Electrohydraulic servo valve capable of being operated by liquid transmission |
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| Publication Number | Publication Date |
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| CN109760826A CN109760826A (en) | 2019-05-17 |
| CN109760826B true CN109760826B (en) | 2023-05-09 |
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Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2716518B1 (en) * | 1994-02-24 | 1996-04-05 | Peugeot | Mechanical control energy transmission device. |
| DE102009045191C5 (en) * | 2009-09-30 | 2020-08-13 | Haldex Brake Products Aktiebolag | Method for operating a braking device for a hydraulically braked towing vehicle |
| CN103144766B (en) * | 2013-03-11 | 2015-04-08 | 西安航空制动科技有限公司 | Electric hydraulic pressure servo valve |
| CN209667360U (en) * | 2019-01-30 | 2019-11-22 | 西安航空制动科技有限公司 | Can liquid pass manipulation electrohydraulic servo valve |
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2019
- 2019-01-30 CN CN201910088985.0A patent/CN109760826B/en active Active
Non-Patent Citations (3)
| Title |
|---|
| 射流偏转板伺服阀的设计与实现;王海玲;;液压与气动(第08期) * |
| 射流管式电液压力伺服阀技术研究;何学工;黄增;金瑶兰;闵丽;;机床与液压(第10期) * |
| 飞机容积控制型液压保险的设计研究;马建峰;;液压与气动(第06期) * |
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