CN107701538B - Hydraulic slide valve structure with built-in piston type valve core - Google Patents
Hydraulic slide valve structure with built-in piston type valve core Download PDFInfo
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- CN107701538B CN107701538B CN201710977829.0A CN201710977829A CN107701538B CN 107701538 B CN107701538 B CN 107701538B CN 201710977829 A CN201710977829 A CN 201710977829A CN 107701538 B CN107701538 B CN 107701538B
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- piston
- valve
- hole
- spool
- valve core
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Classifications
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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
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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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Servomotors (AREA)
- Sliding Valves (AREA)
Abstract
The invention relates to a spool valve structure with a built-in piston type, wherein two ends of a spool are respectively provided with a boss cylinder extending outwards, a central cylinder hole is arranged in the boss cylinder, the bottom of the central cylinder hole is connected with a counter bore in the spool, an oil through hole is formed in the boss cylinder, the oil through hole is communicated with the central cylinder hole, the central cylinder hole is in clearance fit connection with a piston, the bottom of the central cylinder hole is in fit connection with the counter bore, the piston and the oil through hole form a built-in oil pressure control cavity, the piston is propelled to move by the change of oil pressure of the built-in control cavity, and the dynamic response of the whole valve can be improved in response to the movement of the spool. The invention reduces the volume of control cavities at two ends of the valve core, improves the processing manufacturability of the slide valve component of the high-flow jet flow tubular electrohydraulic servo valve, avoids the problem of high coaxiality manufacturability requirement caused by reducing the diameters at two ends of the valve core, and also reduces the number of parts to the minimum. Compared with the similar large-flow jet tube type electrohydraulic servo valve, the valve has the advantage of good dynamic characteristics.
Description
Technical Field
The invention relates to an electrohydraulic servo control valve, in particular to a valve core structure of the electrohydraulic servo control valve.
Background
The electrohydraulic servo valve principle is shown in figure 1, and mainly comprises a torque motor, a hydraulic amplifier, a slide valve component and a feedback component. The torque motor adopts a permanent magnet structure, the spring tube supports the armature jet tube assembly, the motor is isolated from a hydraulic part, and the pre-stage is a hydraulic amplifier. The hydraulic amplifier includes a motor coil 10, an armature 11, a receiver 18, a jet pipe 15, a nozzle 12, and the like. The spool valve assembly includes spool 13, piston 16, filter 17, etc. The feedback assembly includes a feedback rod 14 or the like.
The working principle is as follows: when a control current is input to the motor coil 10, the control flux generated at the armature 11 interacts with the permanent magnetic flux, so that a moment is generated at the armature 11, causing the armature 11 to deflect a small angle proportional to the moment. The jet flow action of the jet pipe 15 and the nozzle 12 causes the pressure at one end of the valve core 13 to rise and the pressure at the other end to drop, the pressure difference is formed at the two ends of the valve core 13, and the valve core 13 moves until the moment generated by the feedback assembly is balanced with the moment of the motor, so that the pressure of the hydraulic amplifier is balanced. At this time, the displacement of the valve core is proportional to the magnitude of the control current, and the output flow of the valve is proportional to the control current.
When the current electrohydraulic control element is in high-flow or high-dynamic demand, the current electrohydraulic control element is usually realized by integrally increasing the structural size of the slide valve or reducing the valve core travel of the slide valve; the mode makes volume and weight of the electrohydraulic control element relatively larger, and simultaneously has higher flow and dynamic requirements on the pilot valve, so that the electrohydraulic control element with the structural form has high manufacturing cost and can only be used in industrial occasions with low weight and volume requirements. Another commonly used structural mode is a mode of adopting a stepped valve core and a floating sleeve, and the mode can improve the dynamic state and the control flow of the electrohydraulic control element, but has the defects of high processing difficulty, multiple component parts and high processing and manufacturing cost. The dynamic and control flow of the electrohydraulic control element can be improved by the external piston and floating sleeve structure of the hydraulic slide valve, but the hydraulic slide valve is large in size and length direction and is generally applied to electrohydraulic servo proportional valves in the industrial field due to the fact that the structure is complex, the parts are more, the machining precision is high in requirements.
Disclosure of Invention
The invention aims to solve the technical problems of poor stability, low dynamic state, jitter of flow characteristic curve and the like of a large-flow electrohydraulic servo valve caused by larger valve core design diameter and larger control cavities at two ends of the valve core, and provides a valve core built-in piston type hydraulic slide valve structure.
In order to achieve the above purpose, the technical scheme of the invention is as follows: the utility model provides a case embeds piston slide valve structure, includes valve pocket, sealing plug, case, piston, the case both ends are equipped with the boss cylinder that extends to the outside respectively, are equipped with central cylinder hole in the boss cylinder, and central cylinder hole bottom meets with the counter bore in the case, and open on the boss cylinder has an oil through hole, and the oil through hole is linked together with central cylinder hole, and the piston is connected in central cylinder hole clearance fit, and sealing plug is connected in central cylinder hole bottom and the counter bore cooperation, sealing plug, piston, oil through hole form a built-in fluid pressure control chamber, advance the piston and remove by the change of fluid pressure in the built-in fluid pressure control chamber, respond to the removal of case, can improve the dynamic response of whole valve.
Further, the sealing plug is in sealing connection with the central cylindrical hole of the valve core through a sealing ring arranged in a sealing groove of the sealing plug.
Further, the fit clearance between the sealing plug and the counter bore of the valve core is 0.03-0.06 mm.
Further, the fit clearance between the central cylindrical hole of the valve core and the piston is 0.001-0.003 mm.
Further, the excircle of the piston is provided with an oil through groove and the end face is of an arc structure, so that the resistance of the piston in the moving process is reduced.
Further, the volume of the built-in oil pressure control cavity is 603mm 3 。
The beneficial effects of the invention are as follows:
1) The method can fill the blank of domestic large-flow jet flow tubular electrohydraulic servo valves, the current domestic jet flow tubular electrohydraulic servo valve flow specification is 2L-200L/min, and the foreign jet flow tubular electrohydraulic servo valve flow specification is 2-400L/min. By adopting the spool-built-in piston type spool valve structure, the volume of control cavities at two ends is reduced, the structure of the spool is integrally reduced, the processing manufacturability of the spool valve component of the high-flow jet flow tubular electro-hydraulic servo valve is improved, and the economic benefit is improved.
2) The invention has simple, compact and practical technical processing measures, low manufacturing cost and effectively improves the dynamic response and stability of the servo valve.
3) The invention has the advantages of simple and clear technology improvement and processing method, and is convenient and easy to master.
The invention adopts a spool-built-in piston type spool valve structure, reduces the volume of control cavities at two ends of the spool, improves the processing manufacturability of the spool valve component of the high-flow jet flow tubular electro-hydraulic servo valve, avoids the problem of high coaxiality manufacturability requirement caused by reducing the diameters at two ends of the spool, and also reduces the number of parts to the minimum. Compared with the similar large-flow jet tube type electrohydraulic servo valve, the valve has the advantage of good dynamic characteristics. The dynamic characteristic of the product reaches 35Hz with amplitude frequency-3 dB and 50Hz with phase frequency-90 degrees under the oil supply pressure of 7 MPa.
Drawings
FIG. 1 is a schematic diagram of a conventional electro-hydraulic servo valve;
FIG. 2 is a partial cross-sectional view of the spool-in-piston spool valve structure of the present invention;
FIG. 3 is a schematic diagram of a built-in piston valve core;
FIG. 4 is a schematic diagram of a piston structure;
fig. 5 is a schematic diagram of a built-in plug structure.
Detailed Description
The invention will be further described with reference to the drawings and examples.
As shown in fig. 2, the spool-embedded piston type spool valve structure of the invention consists of a valve sleeve 1, a sealing plug 2, an O-shaped sealing ring 3, a spool 4 and a piston 5.
The length of bosses at two ends of the valve core 4 is prolonged, two side oil pressure control cavities formed between the original valve core end face and the valve sleeve main hole are built in middle holes of the two bosses at the valve core 4 end face, a cylindrical hole is processed on the excircle of the bosses at two sides of the valve core 4 and is communicated with the middle holes of the valve core, a piston 5 in clearance fit with the middle holes of the valve core 4 is processed, a sealing plug 2 is arranged at the inner side of the middle holes of the valve core 4, and a built-in oil pressure control cavity is formed with the piston 5 and an oil way on the valve core boss, so that the control cavity volume of a large flow valve and the oil passing area of the control cavity are greatly reduced. The piston 5 is pushed to move by the change of the oil pressure in the built-in oil pressure control cavity, and the dynamic response of the whole valve is improved in response to the movement of the valve core 4.
As shown in fig. 3, the total length of the valve core 4 is about 177mm (the total length of the valve sleeve matched with the valve core is about 178 mm), and the outer diameter is about 23mm. Processing a center counter bore 3-1 with the diameter of 8.5mm and the depth of 70.5mm on two sides according to the conventional structure of the valve core, and boring to a diameter of 10.45mm and the depth of 25.2 by a boring cutter on the basis of the center counter bore 3-1 -0.1 A counter bore of mm is coarsely ground and finely ground to 10.5 +0.018 The roughness of the central cylindrical hole 3-2 with the diameter of Ra0.1 is used for installing a sealing plug and a piston. The diameter is 1.6mm, two oil through holes 3-3 which are 13mm away from the end face of the valve core are formed by machining with a drill bit by a bench worker, and the two oil through holes 3-3 are on the same straight line.
As shown in FIG. 4, the total length of the piston 5 is about 14.2, the base hole is used for machining, a gap of 0.001-0.003 mm with a valve core center hole is ensured by means of investigation, the design structures of the oil through groove 4-1 and the end surface circular arc 4-2 are increased mainly for reducing the resistance in the piston moving process, and the threads 4-3 of 2M 2 are designed and mainly used for process installation threads.
As shown in FIG. 5, the design structure of the sealing plug 2 mainly considers the size of the sealing groove 5-1 to meet the compression amount of the selected standard sealing ring so as to ensure the sealing requirement and reduce the internal leakage of the valve. Sealing plug 2 total length 9 -0.1 The tolerance is reduced by the outer diameter of 10.5mm, a clearance of 0.03-0.06 mm is formed between the valve core phi 10.5mm counter bore and the outer diameter of the sealing groove is 7.9 -0.036 mm, width 2.3 +0.1 mm, the arc transition R0.1-R0.3 of the groove bottom and the notch of the sealing groove can avoid the cutting in the assembly process of the sealing groove. The threaded hole 5-2 with the depth of 2M is a process threaded hole and is mainly used for disassembling and assembling the sealing groove. Thus, after the piston 5, the sealing plug 2 and the O-shaped sealing ring 3 are arranged in the valve core center hole, a volume of about 603mm is formed 3 Is provided.
The design improvement is finished in test piece processing, and test verification of static performance and dynamic performance of products is carried out on a hydraulic test bench. The static characteristic curve is smooth, the dynamic characteristic amplitude frequency-3 dB reaches 35Hz, the phase frequency-90 DEG reaches 50Hz, and the improvement effect is obvious.
Claims (4)
1. The utility model provides a case embeds piston type hydraulic slide valve structure, includes valve pocket (1), sealed stifled (2), case (4), piston (5), its characterized in that: the two ends of the valve core (4) are respectively provided with a boss cylinder extending outwards, a central cylinder hole is arranged in the boss cylinder, the bottom of the central cylinder hole is connected with a counter bore in the valve core (4), an oil through hole is formed in the boss cylinder, the oil through hole is communicated with the central cylinder hole, the piston (5) is connected with the bottom of the central cylinder hole in a clearance fit manner, the sealing plug (2) is connected with the counter bore in a fit manner, the sealing plug (2), the piston (5) and the oil through hole form a built-in oil pressure control cavity, the piston (5) is pushed to move by the change of oil pressure in the built-in oil pressure control cavity, and the dynamic response of the whole valve can be improved in response to the movement of the valve core (4); the sealing plug (2) is in sealing connection with the central cylindrical hole of the valve core (4) through a sealing ring arranged in a sealing groove of the sealing plug (2); an oil through groove (4-1) is arranged on the outer circle of the piston (5) and the end face is of an arc (4-2) structure and is used for reducing resistance in the piston moving process.
2. The spool-in-piston type hydraulic spool valve structure according to claim 1, characterized in that: the fit clearance between the sealing plug (2) and the counter bore of the valve core (4) is 0.03-0.06 mm.
3. The spool-in-piston type hydraulic spool valve structure according to claim 1, characterized in that: the fit clearance between the central cylindrical hole of the valve core (4) and the piston (5) is 0.001-0.003 mm.
4. The spool-in-piston type hydraulic spool valve structure according to claim 1, characterized in that: the volume of the built-in oil pressure control cavity is 603mm 3 。
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710977829.0A CN107701538B (en) | 2017-10-17 | 2017-10-17 | Hydraulic slide valve structure with built-in piston type valve core |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710977829.0A CN107701538B (en) | 2017-10-17 | 2017-10-17 | Hydraulic slide valve structure with built-in piston type valve core |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107701538A CN107701538A (en) | 2018-02-16 |
| CN107701538B true CN107701538B (en) | 2023-09-05 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710977829.0A Active CN107701538B (en) | 2017-10-17 | 2017-10-17 | Hydraulic slide valve structure with built-in piston type valve core |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN107701538B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113685385B (en) * | 2021-06-24 | 2022-04-15 | 扬州大学 | Hydraulic system oil way control piece and machining method thereof |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0835502A (en) * | 1994-07-26 | 1996-02-06 | Hitachi Constr Mach Co Ltd | Directional control valve device |
| US5832808A (en) * | 1994-08-05 | 1998-11-10 | Komatsu Ltd. | Directional control valve unit |
| CN2851675Y (en) * | 2005-07-22 | 2006-12-27 | 陈镇汉 | Electro-hydraulic servo valve for load pressure feedback |
| 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 |
| CN103195766A (en) * | 2013-04-01 | 2013-07-10 | 西安双特智能传动有限公司 | Valve bank and method for controlling hydraulic retarder and automatic hydraulic retarder comprising same |
| CN104595271A (en) * | 2015-01-29 | 2015-05-06 | 南京萨伯工业设计研究院有限公司 | Anti-swing control method suitable for bidirectional hydraulic loop |
| CN204476911U (en) * | 2015-03-16 | 2015-07-15 | 武汉科技大学 | A kind of high frequency high linearity jet pipe type electrohydraulic control |
-
2017
- 2017-10-17 CN CN201710977829.0A patent/CN107701538B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0835502A (en) * | 1994-07-26 | 1996-02-06 | Hitachi Constr Mach Co Ltd | Directional control valve device |
| US5832808A (en) * | 1994-08-05 | 1998-11-10 | Komatsu Ltd. | Directional control valve unit |
| CN2851675Y (en) * | 2005-07-22 | 2006-12-27 | 陈镇汉 | Electro-hydraulic servo valve for load pressure feedback |
| 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 |
| CN103195766A (en) * | 2013-04-01 | 2013-07-10 | 西安双特智能传动有限公司 | Valve bank and method for controlling hydraulic retarder and automatic hydraulic retarder comprising same |
| CN104595271A (en) * | 2015-01-29 | 2015-05-06 | 南京萨伯工业设计研究院有限公司 | Anti-swing control method suitable for bidirectional hydraulic loop |
| CN204476911U (en) * | 2015-03-16 | 2015-07-15 | 武汉科技大学 | A kind of high frequency high linearity jet pipe type electrohydraulic control |
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| Publication number | Publication date |
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| CN107701538A (en) | 2018-02-16 |
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