CN102616228B - Pressure type electro-hydraulic servo valve system for brake - Google Patents
Pressure type electro-hydraulic servo valve system for brake Download PDFInfo
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- CN102616228B CN102616228B CN201210103826.1A CN201210103826A CN102616228B CN 102616228 B CN102616228 B CN 102616228B CN 201210103826 A CN201210103826 A CN 201210103826A CN 102616228 B CN102616228 B CN 102616228B
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- pressure
- pressure servo
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- valve
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- 210000002445 nipple Anatomy 0.000 claims description 13
- 238000005507 spraying Methods 0.000 claims description 13
- 238000000034 method Methods 0.000 description 6
- 238000005516 engineering process Methods 0.000 description 4
- 239000000446 fuel Substances 0.000 description 3
- 239000012530 fluid Substances 0.000 description 2
- 108010022579 ATP dependent 26S protease Proteins 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
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- Valves And Accessory Devices For Braking Systems (AREA)
Abstract
The embodiment of the invention discloses a pressure type electro-hydraulic servo valve system for brake. The system comprises first pressure servo equipment and second pressure servo equipment sharing an oil inlet and an oil outlet, wherein each piece of pressure servo equipment is provided with a torque motor and a slide valve; a baffle of the torque motor of each piece of pressure servo equipment is located between an upper oil nozzle and a lower oil nozzle; the pressure difference between the baffles of the upper and lower oil nozzles acts on the outer cylindrical surface of a side convex shoulder of the slide valve; and the air inlet pressure acts on the annular surface of a lower convex shoulder of the slide valve. To perfect the scheme, the system also comprises a zero spring which is connected to the annular surface of an upper convex shoulder of the slide valve. Compared with the existing pressure type electro-hydraulic servo valve, the pressure type electro-hydraulic servo valve system disclosed by the embodiment of the invention has a simpler pipeline; and the zero spring assisting in zero adjustment realizes a technical effect of conveniently performing zero adjustment of the slide valve.
Description
Technical field
The present invention relates to fluid control braking technology field, more particularly, relates to a kind of pressure-type electro-hydraulic pressure servo system for braking.
Background technology
Electronic anti-breaking brake technique is the technology for the vehicle of running at high speed being carried out to braking at a high speed and shortening distance of landing run, this technology is according to the tire momentary velocity of the vehicle and the difference of reference velocity, and the sliding condition of road surface that runs, automatically adjust brake pressure, prevent vehicle snap catch cause lateral deviation etc. not to.
Existing is that left and right pressure-type electrohydraulic servo valve is respectively established one for the pressure-type electro-hydraulic servo valve system braking, and two of left and right valve arranges separately the oil channel structures of oil inlet and return opening, exists the technical matters of connecting line complexity; And described pressure-type electrohydraulic servo valve only relies on the spacing regulation and control of pressure to ensure spool position, and this kind of control methods exist guiding valve zero-bit to regulate inconvenient shortcoming.
Summary of the invention
In view of this, the invention provides a kind of pressure-type electro-hydraulic pressure servo system for braking, succinct to realize pipeline, be convenient to the technique effect returning to zero.
For the pressure-type electro-hydraulic pressure servo system braking, comprising: share the first pressure servo equipment and the second pressure servo equipment of oil inlet and oil outlet, each pressure servo equipment is equipped with torque motor and guiding valve, wherein:
The baffle plate of the torque motor of each pressure servo equipment is located between upper and lower spraying nipple, and the difference of pressure of described upper and lower spraying nipple baffle plate acts on the side convex shoulder outer cylinder of described guiding valve;
Input pressure acts on the lower convex shoulder anchor ring of described guiding valve.
In order to improve such scheme, this system also comprises: zeroing spring, zeroing spring is connected on the upper convex shoulder anchor ring of described guiding valve.
Be arranged at the coarse filter of described the first pressure servo equipment and the second pressure servo equipment room oil inlet.
Be arranged at the thin oil filter between inflow pipeline and upper spraying nipple.
Can find out from above-mentioned technical scheme, pressure-type electro-hydraulic servo valve system in the embodiment of the present invention comprises two pressure servo equipment for braking, in two equipment, share oil inlet and oil return mouth, with existing for comparatively succinct on pipeline compared with pressure-type electrohydraulic servo valve, guiding valve in described pressure servo equipment is provided with the zeroing spring for auxiliary adjustment zero-bit, has realized the technique effect that facilitates guiding valve zeroing.
Brief description of the drawings
In order to be illustrated more clearly in the embodiment of the present invention or technical scheme of the prior art, to the accompanying drawing of required use in embodiment or description of the Prior Art be briefly described below, apparently, accompanying drawing in the following describes is only some embodiments of the present invention, for those of ordinary skill in the art, do not paying under the prerequisite of creative work, can also obtain according to these accompanying drawings other accompanying drawing.
Fig. 1 is the disclosed a kind of pressure-type electro-hydraulic pressure servo system structural representation for braking of the embodiment of the present invention;
Fig. 2 is the disclosed a kind of pressure-type electro-hydraulic pressure servo system sliding valve structure schematic diagram for braking of the embodiment of the present invention.
Detailed description of the invention
Below in conjunction with the accompanying drawing in the embodiment of the present invention, the technical scheme in the embodiment of the present invention is clearly and completely described, obviously, described embodiment is only the present invention's part embodiment, instead of whole embodiment.Based on the embodiment in the present invention, those of ordinary skill in the art, not making the every other embodiment obtaining under creative work prerequisite, belong to the scope of protection of the invention.
The embodiment of the invention discloses a kind of pressure-type electro-hydraulic pressure servo system for braking, succinct to realize pipeline, be convenient to the technique effect returning to zero.
Fig. 1 shows a kind of pressure-type electro-hydraulic pressure servo system for braking, and describes: comprising in conjunction with the sliding valve structure in Fig. 2:
Share the first pressure servo equipment 3 and the second pressure servo equipment 4 of oil inlet 1 and oil outlet 2, describe as an example of the first pressure servo equipment on right side example, the 26S Proteasome Structure and Function of described the second pressure servo equipment is similar, repeats no more and detailed mark:
Described the first pressure servo equipment is equipped with torque motor 5, guiding valve 6 and zeroing spring 7, wherein:
The baffle plate of described torque motor 5 is located between upper and lower spraying nipple, and the difference of pressure of described upper and lower spraying nipple baffle plate 8 acts on the side convex shoulder outer cylinder 9 of described guiding valve 6;
Zeroing spring 7 acts on the upper convex shoulder anchor ring 10 of described guiding valve 6 with load pressure;
Input pressure acts on the lower convex shoulder anchor ring 11 of described guiding valve 6.
In Fig. 1, also show: the coarse filter 12 that is arranged at oil inlet between described the first pressure servo equipment 3 and the second pressure servo equipment 4.
Be arranged at the thin oil filter 15 between inflow pipeline 13 and upper spraying nipple 14.
This System Working Principle describes as an example of the first pressure servo equipment on right side example:
High pressure oil enters after the coarse oil filter 12 of oil inlet 1 filters, and is divided into two-way, enters respectively left and right sides servovalve;
Enter a high pressure oil part for the first pressure servo equipment 3 after thin oil filter 15 filters, enter first segment discharge orifice 16 and second section head piece 17 along two oil circuits respectively;
After the step-down of cutoff port, be divided into two-way, a road flows to the ring surface at guiding valve 6 two ends, and another road enters spraying nipple 14, and after gap 18 throttlings of spraying nipple 14 and torque motor 5, the solenoid valve 19 of flowing through, flows back to fuel tank along oil return line 20;
Enter another part operating fluid of guiding valve 6, enter the fuel supply chamber 25 of guiding valve 6, and aperture 21 on spool is communicated with guiding valve epicoele 22.
In the time that servovalve 3 does not have electric current, torque motor 5 baffle plates are in meta, and upper spraying nipple and lower spraying nipple pressure equates, guiding valve 6 under the effect of zeroing spring 7 in the next;
The oil back chamber 23 of guiding valve 6 and brake chamber 24 UNICOMs, brake chamber 24 pressure (control presssure of valve) equal oil back chamber 23 pressure;
In order to form contrast, input an electric current as example taking the second pressure servo equipment, as can be seen: described torque motor 5 baffle plates deflect down, two nozzle chambers produce difference of pressure, difference of pressure acts on the side convex shoulder outer cylinder 9 of guiding valve 6, guiding valve is moved up, reduce gradually the throttling action between fuel supply chamber 25 and brake chamber 24, chamber 24 pressure rises that make to brake, also make guiding valve epicoele 22 pressure rises, form inverse feedback, hinder valve core movement, in the time of effect balance on guiding valve, guiding valve is in a position, a corresponding brake cavity pressure.Therefore the electric current of, controlling described servovalve 6 is directly proportional to brake chamber 24 pressure.
When to servovalve input rated current, the nozzle pressure official post guiding valve 6 producing continues to move up, and blocking-up brake chamber 24 and oil back chamber 23, links up fuel supply chamber 25 and brake chamber 24, brake chamber 24 pressure approach charge oil pressure, thereby the pressure while having completed brake regulates.
In addition, not mark in the drawings of the housing that is installed in respectively described the first pressure servo equipment and the second pressure servo equipment periphery.
In sum:
Pressure-type electro-hydraulic servo valve system in the embodiment of the present invention comprises two pressure servo equipment for braking, in two equipment, share oil inlet and oil return mouth, with existing for comparatively succinct on pipeline compared with pressure-type electrohydraulic servo valve, guiding valve in described pressure servo equipment is provided with the zeroing spring for auxiliary adjustment zero-bit, has realized the technique effect that facilitates guiding valve zeroing.
In this specification sheets, each embodiment adopts the mode of going forward one by one to describe, and what each embodiment stressed is and the difference of other embodiment, between each embodiment identical similar part mutually referring to.
To the above-mentioned explanation of the disclosed embodiments, make professional and technical personnel in the field can realize or use the present invention.To be apparent for those skilled in the art to the multiple amendment of these embodiment, General Principle as defined herein can, in the case of not departing from the spirit or scope of the embodiment of the present invention, realize in other embodiments.Therefore, the embodiment of the present invention will can not be restricted to these embodiment shown in this article, but will meet the widest scope consistent with principle disclosed herein and features of novelty.
Claims (4)
1. the pressure-type electro-hydraulic pressure servo system for braking, it is characterized in that, comprise: share the first pressure servo equipment and the second pressure servo equipment of oil inlet and oil outlet, each pressure servo equipment is equipped with torque motor, guiding valve and zeroing spring, wherein:
The baffle plate of the torque motor of each pressure servo equipment is located between upper and lower spraying nipple, and the difference of pressure of described upper and lower spraying nipple baffle plate acts on the side convex shoulder outer cylinder of described guiding valve;
Input pressure acts on the lower convex shoulder anchor ring of described guiding valve;
Zeroing spring is connected on the upper convex shoulder anchor ring of described guiding valve.
2. the system as claimed in claim 1, is characterized in that, also comprises: the coarse filter that is arranged at described the first pressure servo equipment and the second pressure servo equipment room oil inlet.
3. the system as claimed in claim 1, is characterized in that, also comprises: be arranged at the thin oil filter between inflow pipeline and upper spraying nipple.
4. the system as claimed in claim 1, is characterized in that, also comprises: the housing that is installed in respectively described the first pressure servo equipment and the second pressure servo equipment periphery.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210103826.1A CN102616228B (en) | 2012-04-10 | 2012-04-10 | Pressure type electro-hydraulic servo valve system for brake |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210103826.1A CN102616228B (en) | 2012-04-10 | 2012-04-10 | Pressure type electro-hydraulic servo valve system for brake |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102616228A CN102616228A (en) | 2012-08-01 |
| CN102616228B true CN102616228B (en) | 2014-08-20 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210103826.1A Expired - Fee Related CN102616228B (en) | 2012-04-10 | 2012-04-10 | Pressure type electro-hydraulic servo valve system for brake |
Country Status (1)
| Country | Link |
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| CN (1) | CN102616228B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN103144624B (en) * | 2013-03-11 | 2015-05-13 | 西安航空制动科技有限公司 | Brake control valve of airplane |
| CN109250075A (en) * | 2018-09-25 | 2019-01-22 | 陕西飞机工业（集团）有限公司 | A kind of aircraft adaptive braking servo valve module |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5240041A (en) * | 1989-12-28 | 1993-08-31 | Moog Inc. | Synthesized flow-control servovalve |
| CN2775363Y (en) * | 2005-02-02 | 2006-04-26 | 陈镇汉 | Dynamic pressure feedback electrohydraulic servo valve |
| CN202001410U (en) * | 2011-02-28 | 2011-10-05 | 西安陕鼓动力股份有限公司 | Resetting mechanism of hydraulic servo valve |
-
2012
- 2012-04-10 CN CN201210103826.1A patent/CN102616228B/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5240041A (en) * | 1989-12-28 | 1993-08-31 | Moog Inc. | Synthesized flow-control servovalve |
| CN2775363Y (en) * | 2005-02-02 | 2006-04-26 | 陈镇汉 | Dynamic pressure feedback electrohydraulic servo valve |
| CN202001410U (en) * | 2011-02-28 | 2011-10-05 | 西安陕鼓动力股份有限公司 | Resetting mechanism of hydraulic servo valve |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102616228A (en) | 2012-08-01 |
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Address after: 611130 Changan Road, Liucheng, Wenjiang District, Chengdu, Sichuan Province, No. 198 Patentee after: SICHUAN AEROSPACE FENGHUO SERVO CONTROL TECHNOLOGY Co.,Ltd. Address before: 611100 Liucheng Road, Wenjiang, Sichuan, No. Changan Road, No. 198 Patentee before: SICHUAN FENGHUO MACHINERY FACTORY OF CHINA AEROSPACE SCIENCE AND TECHNOLOGY Corp. |
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| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140820 |
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| CF01 | Termination of patent right due to non-payment of annual fee |