CN202001410U - Resetting mechanism of hydraulic servo valve - Google Patents
Resetting mechanism of hydraulic servo valve Download PDFInfo
- Publication number
- CN202001410U CN202001410U CN2011200501331U CN201120050133U CN202001410U CN 202001410 U CN202001410 U CN 202001410U CN 2011200501331 U CN2011200501331 U CN 2011200501331U CN 201120050133 U CN201120050133 U CN 201120050133U CN 202001410 U CN202001410 U CN 202001410U
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- power stage
- valve
- servo
- control chamber
- servovalve
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Abstract
The utility model belongs to the field of servo control elements in hydraulic engineering, in particular to a resetting mechanism of a hydraulic servo valve. The resetting mechanism at least comprises a power stage slide valve control cavity and a power stage slide valve core of the servo valve and is characterized in that a compression spring is arranged in the power stage slide valve control cavity; one end of the compression spring is butted with the end side face of the power stage slide valve core; and the other end of the compression spring is butted with the inner end face of the power stage slide valve control cavity. By adopting the resetting mechanism, a piston rod of a servo oil cylinder can be at a prescient and safe working position when faults that an internal feedback rod in the servo valve is fractured, a spray nozzle of the servo valve is plugged because of pollution, or the pressure of an oil supply hydraulic source of the servo valve suddenly falls, the servo valve loses pilot pressure and the like are generated.
Description
Technical field
The utility model belongs to the servo control element field in the oilhydraulic engineering, is specifically related to a kind of resetting-mechanism of hydraulic efficiency servo-valve.
Background technique
Now Chang Yong hydraulic efficiency servo-valve mainly contains the servovalve of jet pipe servo valve and nozzle flapper form, the pilot structure working principle difference of the two, but the working condition of power stage valve core of the spool valve and servo-cylinder is identical.
With the jet pipe servo valve is example, as shown in Figure 1, under normal operation, when servovalve is not controlled electric current 11, jet pipe 7 and nozzle 6 mediate, and two receiving orifice pressure of Receiver 8 equate that the pressure at power stage valve core of the spool valve 2 two ends equates, mediate each oil circuit hole (P
S, T, P
A, P
B) between cut off mutually; After the servovalve coil 10 input control electric currents 11, armature 9 deflects under the comprehensive function of fixing magnetic flux and control magnetic flux, drive jet pipe 7 and nozzle 6 deflections, pressure difference appears in two receiving orifices of Receiver 8, make power stage valve core of the spool valve 2 two ends pressure reduction occur, this pressure reduction promotes power stage valve core of the spool valve 2 and moves, driving feedback rod 5 simultaneously moves, deflecting torque when armature 9, reseting torque with elastic part in the torque motor, when the reseting torque of feedback rod 5 reaches balance, the power stage valve core of the spool valve 2 of servovalve rests on the working position, the control mouthful certain aperture of maintenance, export certain flow, the input current of this flow and servovalve exists continuous, linear ratio relation one to one.When servovalve internal feedback bar 5 ruptures, the nozzle 6 of servovalve is blocked because of pollution, two receiving orifices of Receiver all do not have the fuel feeding hydraulic power of pressure or servovalve to fall to press suddenly, servovalve loses pilot pressure and under the situation about breaking down, nozzle 6 is positioned at the neutral position, power stage valve core of the spool valve 2 two ends do not have pilot pressure poor, thereby cause power stage valve core of the spool valve 2 to be in uncertain position, the follow-up work of servo-cylinder piston rod also is in unknown state thereupon, is unfavorable for that very the safety of producing carries out smoothly.
Servovalve for the nozzle flapper form, because of the working condition with above-mentioned jet pipe servo valve power stage valve core of the spool valve and servo-cylinder is identical, so the servovalve of working as the nozzle flapper form occurs, and the internal feedback bar takes place to rupture or the fuel feeding hydraulic power of servovalve falls to press suddenly, when servovalve lost pilot pressure, above-mentioned same production accident also can appear.
Summary of the invention
Defective or deficiency at prior art, the purpose of this utility model is to provide a kind of resetting-mechanism of hydraulic efficiency servo-valve, make the piston rod of hydraulic servo oil cylinder occur that servovalve internal feedback bar ruptures, the nozzle of servovalve is blocked because of pollution or the fuel feeding hydraulic power of servovalve falls to press suddenly, servovalve can be in precognition, safe working position when losing fault such as pilot pressure.
For realizing above-mentioned technical assignment, the utility model is taked following technical solution:
A kind of resetting-mechanism of hydraulic efficiency servo-valve, at least the power stage guiding valve control chamber and the power stage valve core of the spool valve that is positioned at power stage guiding valve control chamber that comprise hydraulic efficiency servo-valve, it is characterized in that, one pressure spring is installed in the power stage guiding valve control chamber, the end side surface of this pressure spring one end and power stage valve core of the spool valve connects, and the other end and power stage guiding valve control chamber interior edge face connect.
Other technologies of the present utility model are characterized as:
Establish a spring pedestal between described pressure spring and the power stage guiding valve control chamber interior edge face, the position of docking with pressure spring on the described spring pedestal is fluted.
Described spring pedestal or be installed on pressure spring and power stage guiding valve control chamber interior edge face between, or with power stage guiding valve control chamber inner end wall be one.
The resetting-mechanism of hydraulic efficiency servo-valve provided by the utility model, when the servovalve proper functioning, the elastic force of pressure spring is very little with respect to hydraulic coupling, and its elastic force effect can be ignored; When the nozzle of servovalve is blocked because of pollution or the fuel feeding hydraulic power of servovalve falls faults such as pressure suddenly and causes the spool two ends of power stage guiding valve not have pilot pressure or under the situation of feedback rod fracture failure, the pretightening force of pressure spring can make the spool secundly, guarantee that servovalve is fuel-displaced from as can be known a control port in advance, actuator is remained on the safe position.The resetting-mechanism of this servovalve can require optionally to be assemblied in arbitrary end of power stage valve core of the spool valve according to the real work of servo-cylinder.
Description of drawings
Fig. 1 is a structural representation of the present utility model;
Among the figure: P
SMouth connects fuel feeding, and the T mouth takes back oil, P
AConnect a chamber of servo-cylinder, P
BConnect another chamber of servo-cylinder; The 1-pressure spring, the 2-spool, 3-power stage guiding valve control chamber, the 4-spring pedestal, the 5-feedback rod, the 6-nozzle, the 7-jet pipe, the 8-Receiver, 9-armature, the 10-coil, 11-controls electric current.
The utility model is described in further detail below in conjunction with embodiment and accompanying drawing.
Embodiment
The resetting-mechanism of hydraulic efficiency servo-valve provided by the utility model, at least the power stage guiding valve control chamber 3 and the power stage valve core of the spool valve 2 that is installed in the power stage guiding valve control chamber 3 that comprise hydraulic efficiency servo-valve, it is characterized in that, one pressure spring 1 is installed in the power stage guiding valve control chamber 3, the end side surface of these pressure spring 1 one ends and power stage valve core of the spool valve 2 connects, and the other end and power stage guiding valve control chamber 3 interior edge faces connect.Mounting point for better limit compression spring, guarantee the work that it does not thoroughly disturb other elements, establish a spring pedestal 4 between described pressure spring 1 and power stage guiding valve control chamber 3 interior edge faces, the position of docking with pressure spring 1 on the described spring pedestal 4 is fluted.In the production process of reality, spring pedestal 4 or be installed on pressure spring 1 and power stage guiding valve control chamber 3 interior edge faces between, or make with power stage guiding valve control chamber 3 inner end wall and to become one.
With the jet pipe servo valve is example, as shown in Figure 1, docks a pressure spring 1 at an interior edge face of power stage guiding valve control chamber 3, and the other end of this pressure spring 1 and power stage valve core of the spool valve 2 side end faces connect.In order to reach better technique effect, can between pressure spring 1 and power stage guiding valve control chamber 3 interior edge faces, establish a spring pedestal 4, the position of docking with pressure spring 1 on the described spring pedestal 4 is fluted.Spring pedestal 4 wherein or be installed on pressure spring 1 and power stage guiding valve control chamber 3 interior edge faces between, or with power stage guiding valve control chamber 3 inner end wall be one.Under the servovalve normal operation, because of the elastic force of used pressure spring 1 has only a few kgf values usually, its elastic force is very little with respect to hydraulic coupling, and the elastic force effect of 1 pair of power stage valve core of the spool valve 2 of pressure spring can be ignored.
When servovalve internal feedback bar 5 ruptures, there is pilot pressure much at one at power stage valve core of the spool valve 2 two ends, the deflecting torque of the armature 9 and reseting torque of the elastic part in the torque motor balances each other or the nozzle 6 of servovalve is blocked because of pollution, the deflecting torque of armature 9 and the reseting torque of the elastic part in the torque motor balance each other, the fuel feeding hydraulic power of servovalve falls to press suddenly, the reseting torque of feedback rod 5 adds the deflecting torque of upper armature 9, balance each other with the reseting torque of elastic part in the torque motor, and make power stage valve core of the spool valve 2 two ends not have under the situation of pilot pressure, nozzle 6 is positioned at the neutral position, power stage valve core of the spool valve 2 two ends do not have pilot pressure poor, the stressed elastic force that is mainly pressure spring 1 of power stage valve core of the spool valve 2, power stage valve core of the spool valve 2 is pulled to the other end under the effect of pressure spring 1 elastic force, and then guarantee that servovalve is fuel-displaced from as can be known a control port in advance, actuator's (as servo-cylinder) is remained on the safe position.The resetting-mechanism of this servovalve can require optionally to be assemblied in arbitrary end of power stage valve core of the spool valve according to the real work of servo-cylinder.
As shown in Figure 1, when pressure spring 1 was installed in left position, under pressure spring 1 elastic force effect, power stage valve core of the spool valve 2 can be pulled to right-hand member, P under this state
AMouth and P
SMouth communicates P
BMouth and T mouth communicate.When pressure spring 1 was installed in location right, under pressure spring 1 elastic force effect, power stage valve core of the spool valve 2 can be pulled to left end, P under this state
AMouth communicates P with the T mouth
BMouth and P
SMouth communicates.
Servovalve for the nozzle flapper form, the working condition of its power stage valve core of the spool valve and servo-cylinder is identical, when appearring in the servovalve of nozzle flapper form, the internal feedback bar ruptures, or the fuel feeding hydraulic power of servovalve falls to press suddenly, when servovalve loses pilot pressure, can use solution of the present utility model to improve the job security of hydraulic system equally.
Claims (3)
1. the resetting-mechanism of a hydraulic efficiency servo-valve, at least comprise the power stage guiding valve control chamber (3) of hydraulic efficiency servo-valve and be positioned at the power stage valve core of the spool valve (2) of power stage guiding valve control chamber (3), it is characterized in that, one pressure spring (1) is installed in the power stage guiding valve control chamber (3), the end side surface of this pressure spring (1) one end and power stage valve core of the spool valve (2) connects, and the other end and power stage guiding valve control chamber (3) interior edge face connect.
2. the resetting-mechanism of hydraulic efficiency servo-valve as claimed in claim 1, it is characterized in that, establish a spring pedestal (4) between described pressure spring (1) and power stage guiding valve control chamber (3) interior edge face, it is fluted that this spring pedestal (4) is gone up the position of docking with pressure spring (1).
3. the resetting-mechanism of hydraulic efficiency servo-valve as claimed in claim 2, it is characterized in that, described spring pedestal (4) or be installed on pressure spring (1) and power stage guiding valve control chamber (3) interior edge face between, or with power stage guiding valve control chamber (3) inner end wall be one.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011200501331U CN202001410U (en) | 2011-02-28 | 2011-02-28 | Resetting mechanism of hydraulic servo valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011200501331U CN202001410U (en) | 2011-02-28 | 2011-02-28 | Resetting mechanism of hydraulic servo valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202001410U true CN202001410U (en) | 2011-10-05 |
Family
ID=44704153
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011200501331U Expired - Lifetime CN202001410U (en) | 2011-02-28 | 2011-02-28 | Resetting mechanism of hydraulic servo valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202001410U (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102616228A (en) * | 2012-04-10 | 2012-08-01 | 中国航天科技集团公司烽火机械厂 | Pressure type electro-hydraulic servo valve system for brake |
| CN106640804A (en) * | 2015-10-30 | 2017-05-10 | 北京精密机电控制设备研究所 | Pre-stage split press-fit type jet pipe servo valve |
| CN106949115A (en) * | 2017-04-15 | 2017-07-14 | 广西南宁超网网络科技有限责任公司 | A kind of SERVO CONTROL is with simple and efficient calibration resetting means |
| CN107588052A (en) * | 2017-10-17 | 2018-01-16 | 上海衡拓液压控制技术有限公司 | Valve element built-in piston formula big flow force feedback jet pipe two-stage electrohydraulic servo valve |
| CN107701538A (en) * | 2017-10-17 | 2018-02-16 | 上海衡拓液压控制技术有限公司 | Valve element built-in piston formula hydraulic efficiency slide valve structure |
| 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 |
| CN112196854A (en) * | 2020-09-19 | 2021-01-08 | 安徽工程大学 | Two-stage electro-hydraulic servo valve |
| CN113153849A (en) * | 2021-04-25 | 2021-07-23 | 陈惠波 | Hydraulic servo valve |
-
2011
- 2011-02-28 CN CN2011200501331U patent/CN202001410U/en not_active Expired - Lifetime
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102616228B (en) * | 2012-04-10 | 2014-08-20 | 中国航天科技集团公司烽火机械厂 | Pressure type electro-hydraulic servo valve system for brake |
| CN102616228A (en) * | 2012-04-10 | 2012-08-01 | 中国航天科技集团公司烽火机械厂 | Pressure type electro-hydraulic servo valve system for brake |
| CN106640804B (en) * | 2015-10-30 | 2018-11-30 | 北京精密机电控制设备研究所 | A kind of prestage fission pressing type jet pipe servo valve |
| CN106640804A (en) * | 2015-10-30 | 2017-05-10 | 北京精密机电控制设备研究所 | Pre-stage split press-fit type jet pipe servo valve |
| CN106949115A (en) * | 2017-04-15 | 2017-07-14 | 广西南宁超网网络科技有限责任公司 | A kind of SERVO CONTROL is with simple and efficient calibration resetting means |
| CN107701538A (en) * | 2017-10-17 | 2018-02-16 | 上海衡拓液压控制技术有限公司 | Valve element built-in piston formula hydraulic efficiency slide valve structure |
| CN107588052A (en) * | 2017-10-17 | 2018-01-16 | 上海衡拓液压控制技术有限公司 | Valve element built-in piston formula big flow force feedback jet pipe two-stage electrohydraulic servo valve |
| CN107701538B (en) * | 2017-10-17 | 2023-09-05 | 上海衡拓液压控制技术有限公司 | Hydraulic slide valve structure with built-in piston type valve core |
| CN107588052B (en) * | 2017-10-17 | 2023-09-12 | 上海衡拓液压控制技术有限公司 | Two-stage electrohydraulic servo valve with built-in valve core and piston type high-flow force feedback jet pipe |
| 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 |
| CN112196854A (en) * | 2020-09-19 | 2021-01-08 | 安徽工程大学 | Two-stage electro-hydraulic servo valve |
| CN113153849A (en) * | 2021-04-25 | 2021-07-23 | 陈惠波 | Hydraulic servo valve |
| CN113153849B (en) * | 2021-04-25 | 2023-09-15 | 沈阳帕维电力技术有限公司 | Hydraulic servo valve |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term | ||
| CX01 | Expiry of patent term |
Granted publication date: 20111005 |