CN112324975A - Axial-flow type electromagnetic pilot pressure difference driving large-flow control valve - Google Patents
Axial-flow type electromagnetic pilot pressure difference driving large-flow control valve Download PDFInfo
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- CN112324975A CN112324975A CN202011301866.8A CN202011301866A CN112324975A CN 112324975 A CN112324975 A CN 112324975A CN 202011301866 A CN202011301866 A CN 202011301866A CN 112324975 A CN112324975 A CN 112324975A
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02K—JET-PROPULSION PLANTS
- F02K9/00—Rocket-engine plants, i.e. plants carrying both fuel and oxidant therefor; Control thereof
- F02K9/42—Rocket-engine plants, i.e. plants carrying both fuel and oxidant therefor; Control thereof using liquid or gaseous propellants
- F02K9/44—Feeding propellants
- F02K9/56—Control
- F02K9/58—Propellant feed 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
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/20—Excess-flow valves
- F16K17/22—Excess-flow valves actuated by the difference of pressure between two places in the flow line
- F16K17/24—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member
- F16K17/28—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only
- F16K17/30—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only spring-loaded
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
In order to realize the quick on-off control problem of high-pressure large-flow media under the condition of no external control gas source and simultaneously consider the small and light structure to meet the performance index requirements of a quick-response high-performance attitude control engine, the invention provides an axial electromagnetic pilot pressure difference driving large-flow control valve.
Description
Technical Field
The invention relates to an axial-flow electromagnetic pilot pressure difference driving large-flow control valve which can be used as a high-pressure large-flow medium on-off control valve of a liquid rocket engine, a satellite on-orbit execution power system and a ground test system and is used for controlling the starting and the shutdown of the engine. The invention can realize on-off control of large flow and high pressure propellant supply under the condition of no external control gas source, and realizes quick response control of opening and closing while meeting the requirements of small and light structure.
Background
In the development of a certain pre-developed model quick-response high-performance attitude control engine, a control valve is required by a system to meet the requirements of large flow and high pressure of a large-thrust engine with more than 3000N, and meanwhile, the quick response of opening and closing and the small and light structure are ensured. The engine is limited by the assembly structure and has no control gas supply, so that an electric air valve structure scheme cannot be adopted. The electromagnetic valve scheme is adopted, in order to meet the working requirements of high flow and high pressure, the electromagnetic valve needs to be designed with a large drift diameter, the action requirement can be met only by large electromagnetic attraction force and an electromagnet structure, the designed electromagnetic valve is slow in opening and closing response, large in structural size and weight and incapable of meeting the performance index requirement of a quick-response high-performance attitude control engine.
In order to meet the control requirements of a fast-response high-performance engine under the conditions of high flow and high pressure, an axial-flow electromagnetic pilot pressure difference driving large-flow control valve structure is provided, the fast response control of opening and closing of a high-pressure large-flow medium is realized by utilizing a two-stage valve structure and the gradient difference of a pressure field formed by the medium in a flow channel, the product development test is completed, the control valve is fast in response after the engine test and examination, and the development and design requirements of the high-performance engine are met.
Disclosure of Invention
The invention provides an axial-flow electromagnetic pilot pressure difference driven large-flow control valve, which aims to realize the problem of quick on-off control of a high-pressure large-flow medium under the condition of no external control air source and simultaneously consider the small and light structure so as to meet the performance index requirements of a quick-response high-performance attitude control engine.
The technical solution of the invention is as follows:
the axial-flow type electromagnetic pilot pressure difference driving large-flow control valve is characterized in that: the electromagnetic auxiliary valve and the differential pressure main valve are integrated into a whole along the axial direction;
the electromagnetic auxiliary valve comprises an auxiliary valve body, an electromagnetic coil, an auxiliary valve core, an auxiliary return spring and an auxiliary valve seat;
the differential pressure main valve comprises a main valve body, a main valve core, a main return spring, a main valve seat and a retainer;
an inlet nozzle is integrated on the auxiliary valve body and is used as an inlet of the control valve; the auxiliary valve core is arranged in the auxiliary valve body; the electromagnetic coil is sleeved outside the auxiliary valve core and is positioned between the auxiliary valve body and the auxiliary valve core; one end of the auxiliary return spring is connected/contacted with the auxiliary valve body, and the other end of the auxiliary return spring is connected/contacted with one end of the auxiliary valve core; the auxiliary valve seat is integrated in the main valve body and is positioned on the central axis of the main valve body;
an outlet connecting nozzle is integrated on the main valve body and is used as an outlet of the control valve; the main valve core, the reset main spring and the retainer are sequentially arranged in the main valve body along the axial direction, and the main valve core is closer to the electromagnetic auxiliary valve; one end of the main valve core close to the electromagnetic auxiliary valve is a piston section, and the other end of the main valve core is a sealing section; the outer wall of the piston section of the main valve core is matched with the inner wall of the main valve body in a guiding way, and a piston cavity is formed; the main valve seat is integrated on the inner wall of the main valve core close to the outlet nozzle;
a first medium flow channel hole is formed in the auxiliary valve core, and a second medium flow channel hole is formed in the side wall of the main valve body; one end of the first medium flow channel hole is communicated with the inlet filler head, and the other end of the first medium flow channel hole is communicated with the second medium flow channel hole; the first medium flow channel hole and the second medium flow channel hole form a large-drift-diameter main flow channel of the control valve; the main valve seat and the main valve core form a switch sealing pair of a medium main flow passage;
an auxiliary flow passage hole is arranged at the central shaft position of the main valve body, axially penetrates through the auxiliary valve seat and is communicated with the piston cavity; a central shaft of the main valve core is also sequentially provided with a throttling nail with a small flow limiting hole and a slender hole; one end of the elongated hole is communicated with the piston cavity through the small flow limiting hole, and the other end of the elongated hole is communicated with the outlet nozzle; the elongated hole, the small flow limiting hole and the secondary flow passage hole jointly form a secondary flow passage of the control valve, and the secondary valve seat and the secondary valve core form a switch sealing pair of the secondary flow passage.
Further, the diameter of the main valve core piston section is larger than the sealing diameter of the main valve core seat.
Furthermore, the aperture of the small flow-limiting hole on the throttling nail is designed in a matching mode according to parameters of the drift diameter of the auxiliary valve seat, the diameter of the piston section of the main valve core, the volume of the piston cavity and the sealing diameter of the main valve seat of the main valve core.
Compared with the prior art, the invention has the advantages that:
1. the invention adopts an axial integrated design structure of a primary small-drift-diameter electromagnetic auxiliary valve and a secondary large-drift-diameter pressure difference main valve, utilizes electromagnetic attraction to drive the primary small-drift-diameter electromagnetic auxiliary valve to open, utilizes medium pressure difference formed by working media after the electromagnetic auxiliary valve is opened to drive the secondary large-drift-diameter main valve to open, has high medium pressure difference forming speed and large actuating power, can quickly drive the large-drift-diameter main valve to open, and meets the medium on-off control requirements of high pressure and large flow.
2. The invention utilizes the pressure difference formed by medium flow under the condition of no external control air source to drive the main valve core to open or close, the medium pressure difference is formed quickly, the actuation power is large, the quick response of the opening and closing of the large-diameter main valve is ensured, an important technical scheme is provided for the development of a quick-response and high-thrust attitude and orbit control engine control valve, and the invention has obvious advantages in a system without air supply and with high response speed requirement.
3. The invention sets a slender hole on the central shaft of the main valve core, and installs a throttle pin with a small flow-limiting hole, the smaller the aperture of the small hole is, the faster the pressure building speed of the main valve core piston is when opening, and the more favorable the quick response of opening; conversely, the larger the aperture of the small hole is, the faster the pressure relief speed of the main valve core piston cavity is discharged when the main valve core piston cavity is closed is, and the closing response is facilitated; the aperture of the small flow limiting hole can be adjusted by replacing the throttling nail with the small flow limiting hole with different apertures, so that the opening response and the closing response are both optimized and matched, and meanwhile, the quick response of the engine and the quick response of the engine can be subjected to emphasis adjustment according to the actual requirements of the engine.
4. The invention adopts an axial layout structure, a differential pressure main valve and an electromagnetic auxiliary valve adopt an integrated axial flow type integrated layout structure, an inlet connecting nozzle is integrated on an auxiliary valve body of the electromagnetic auxiliary valve, an outlet connecting nozzle is integrated on a main valve body of the differential pressure main valve, the electromagnetic auxiliary valve and the differential pressure main valve share a medium auxiliary flow passage and a medium main flow passage, the structure is in axial flow type arrangement, the whole structure is compact, the action directions of the auxiliary valve core and the main valve core and the medium flow direction are axial, the guide structure and the action reliability are high, and the structural layout is matched and coordinated.
Drawings
Fig. 1 is a structural schematic diagram of a large-flow control valve driven by axial-flow type electromagnetic pilot pressure difference.
Reference numerals:
1-main valve body; 2-the auxiliary valve body; 3-an electromagnetic coil; 4-auxiliary valve core; 5-a return auxiliary spring; 6-main valve core; 7-return main spring; 8-a throttling nail; 9-O-shaped rubber sealing rings; 10-a cage; 11-a main flow channel; 12-an auxiliary flow channel; 13-a counter-valve seat; 14-main valve seat; 15-small restriction orifice; 16-a piston cavity; 17-elongated apertures; 20-a first medium flow channel hole; 21-a second medium flow channel hole; 22-secondary flow channel hole.
Detailed Description
The invention is further described below with reference to the accompanying drawings.
As shown in fig. 1, the axial-flow type electromagnetic pilot differential pressure drive large-flow control valve provided by the present invention integrally adopts an axial-flow type two-stage pilot structure, and includes a small-bore electromagnetic auxiliary valve and a large-bore differential pressure main valve which are coaxially arranged along an axial direction and integrated into a whole, an inlet of the electromagnetic auxiliary valve is an inlet of the control valve, and an outlet of the differential pressure main valve is an outlet of the control valve.
The electromagnetic auxiliary valve comprises an auxiliary valve body 2, an electromagnetic coil 3, an auxiliary valve core 4, an auxiliary return spring 5 and an auxiliary valve seat 13.
The differential pressure main valve comprises a main valve body 1, a main valve core 6, a main return spring 7, a main valve seat 14 and a retainer 10.
An inlet nozzle is integrated on the auxiliary valve body 2 and is used as a control valve inlet and is connected with a medium inlet; the auxiliary valve core 4 is arranged in the cavity of the auxiliary valve body 2; the electromagnetic coil 3 is arranged between the auxiliary valve body 2 and the auxiliary valve core 4 and sleeved outside the auxiliary valve core 4; the auxiliary return spring 5 is arranged between the auxiliary valve body 2 and the auxiliary valve core 4, one end of the auxiliary return spring 5 is connected/contacted with the auxiliary valve body 2, the other end of the auxiliary return spring 5 is connected/contacted with one end of the auxiliary valve core 4, and the auxiliary return spring 5 is used for ensuring that the auxiliary valve core 4 is in a closed and sealed state under the condition that the control valve is not electrified; the auxiliary valve seat 13 is integrally arranged in the main valve body 1 and is positioned on the central axis of the main valve body 1.
An outlet nozzle is integrated on the main valve body 1 and is used as an outlet of the control valve; the main valve core 6, the main return spring 7 and the retainer 10 are sequentially arranged in the middle cavity of the main valve body 1 along the axial direction, the main valve core 6 is closer to the electromagnetic auxiliary valve, the retainer 10 is positioned at the outlet of the control valve, and the main return spring 7 is used for ensuring that the main valve core 6 is in a closed and sealed state under the condition that the control valve is not electrified; one end of the main valve core 6 close to the electromagnetic auxiliary valve is a piston section, and the other end is a sealing section; the outer wall of the piston section of the main valve core 6 is matched with the inner wall of the main valve body 1 in a guiding way, and a piston cavity 16 is formed between the piston section of the main valve core 6 and the main valve body 1 after the sealing of an O-shaped rubber sealing ring 9; main valve seat 14 is integrally provided on the inner wall of main valve element 6 near the outlet, and when main valve element 6 is movable along the central axis of main valve body 1, it can seal main valve seat 14 when it moves to the position where its sealing section abuts main valve seat 14.
A first medium flow passage hole 20 with a large diameter is provided in the sub-valve body 4, and a second medium flow passage hole 21 with a large diameter is provided in the side wall of the main valve body 1; one end of the first medium flow passage hole 20 communicates with the control valve inlet, and the other end of the first medium flow passage hole 21 communicates with the second medium flow passage hole 21; the first medium flow channel hole 20 and the second medium flow channel hole 21 constitute a large-diameter medium main flow channel 11 of the control valve; the main valve seat 14 and the main valve element 6 form a switching sealing pair of the medium main flow channel 11.
A secondary flow passage hole 22 is provided at a central axis position of the main valve body 1, and the secondary flow passage hole 22 axially penetrates the secondary valve seat 13 and communicates with the piston chamber 16; a throttling nail 8 with a small flow limiting hole 15 and an elongated hole 17 are sequentially arranged on a central shaft of the main valve element 6, one end of the elongated hole 17 is communicated with the piston cavity 16 through the small flow limiting hole 15, and the other end of the elongated hole 17 is communicated with an outlet of the control valve; the elongated hole 17, the small flow restriction hole 15, and the sub-flow passage hole 22 together constitute a small-diameter medium sub-flow passage 12 of the control valve, and the sub-valve seat 13 and the sub-valve body 4 constitute a switching seal pair of the medium sub-flow passage 12. The structural design can improve the space utilization rate, shorten the flow path, promote the quick formation of the opening differential pressure and the closing differential pressure at the two ends of the main valve core 6, and improve the response speed of the opening and closing actions of the differential pressure main valve.
The diameter of the piston section of the main valve element 6 is matched with the sealing diameter of the main valve element and is slightly larger than the sealing diameter of the main valve seat of the main valve element, so that after the electromagnetic auxiliary valve is turned off, a medium in a piston cavity 16 at the left end of the main valve element 6 is discharged through the small flow limiting hole 15 and the elongated hole 17 and is quickly decompressed, the main valve element 6 is quickly formed into pressure difference in the closing direction to drive the main valve element 6 to be closed, and stable holding force is provided for the closing and sealing of the main valve element 6 and the main valve seat 14 after the main valve element 6 is closed in.
The aperture of the small flow-limiting hole 15 on the throttling nail 8 can be matched, designed and adjusted according to the parameters of the diameter of the auxiliary valve seat 13 of the electromagnetic auxiliary valve, the diameter of the piston section of the main valve core 6, the volume of the piston cavity 16 and the sealing diameter of the main valve seat of the main valve core, and through the damping effect of the small flow-limiting hole 15 on the throttling nail 8, on one hand, the quick pressure build-up in the piston cavity 16 can be ensured, the pressure difference for axially opening the main valve core 6 is quickly formed, the main valve core 6 is driven to be quickly opened, the medium main flow passage 11 is opened, and the quick; on the other hand, after the electromagnetic auxiliary valve is powered off and the medium auxiliary flow passage 12 is closed, the pressure is quickly released in the piston cavity 16, the pressure difference in the closing direction is formed to drive the main valve element 6 to be quickly closed, the medium main flow passage 11 is closed, and the control valve is ensured to be quickly closed and respond. Since the smaller the aperture of the small restriction hole 15 on the restriction pin 8, the faster the opening response and the slower the closing response, and conversely, the larger the aperture of the small restriction hole 15, the faster the closing response and the slower the opening response. Therefore, the opening response and the closing response can be optimized and matched by replacing the throttling nail 8 with the small throttling hole 15 with different apertures, and the quick response of the engine and the quick response of the shutdown can be adjusted in a weighted manner according to the actual requirements of the engine.
The working principle and the process of the invention are as follows:
the working mode of the invention is power-on opening and power-off closing.
The sealing drift diameter of the auxiliary valve core 4 and the auxiliary valve seat 13 is small, the closing medium force is small, the electromagnetic suction force generated by electrifying the electromagnetic coil 3 can be used for driving the auxiliary valve core 4 to be quickly opened, and the opening of the auxiliary flow passage 12 is realized; after the electromagnetic coil 3 is powered off, the auxiliary valve core 4 is driven to be quickly closed by the acting force and the medium force of the return auxiliary spring 5, so that the auxiliary flow channel 12 is cut off.
The opening and closing direction pressure difference is formed at the two ends of the main valve core 6 after the passage of the auxiliary flow passage 12 is cut off, the main valve core 6 is driven to be rapidly opened and closed, and the opening and cut-off control of the passage of the medium main flow passage 11 is realized.
The specific action process is as follows:
when the valve is not electrified to work, the auxiliary valve core 4 is in a closed position under the action of the reset auxiliary spring 5, the main valve core 6 is in a closed position under the action of the reset main spring 7, medium enters the internal cavity channel of the control valve from the inlet to add medium closing force to the auxiliary valve core 4 and the main valve core 6 (the higher the pressure is, the larger the medium closing force is, the more the valve sealing is facilitated), the auxiliary flow channel 12 is cut off through the closing seal between the auxiliary valve core 4 and the auxiliary valve seat 13, and the main flow channel 11 is cut off through the closing seal between the main valve core 6 and the main valve seat 14;
when the electromagnetic auxiliary valve works, an electromagnetic coil 3 of the electromagnetic auxiliary valve is electrified, so that electromagnetic suction force is generated between an auxiliary valve core 4 and an auxiliary valve body 2, the auxiliary valve core 4 overcomes the spring force and the hydraulic unbalance force of a reset auxiliary spring 5 and moves leftwards, the auxiliary valve core 4 is opened to open an auxiliary flow passage 12, an inlet medium flows into a piston cavity 16 through an auxiliary valve seat 13, under the flow limiting action of a small flow limiting hole 15 in a throttling nail 8, the piston cavity 16 of a main valve core 6 is quickly pressurized, pressure difference in the opening direction is formed at two ends of the main valve core 6 to drive the main valve core 6 to move rightwards, so that the main valve core 6 is opened, a main flow passage 11 is opened, and the;
when the electromagnetic valve does not work, the electromagnetic coil 3 of the electromagnetic auxiliary valve is powered off, the electromagnetic suction force between the auxiliary valve core 4 and the auxiliary valve body 2 disappears, the auxiliary valve core 4 moves rightwards to be closed under the action of the spring force of the reset auxiliary spring 5 and the medium force, the auxiliary valve core 4 and the auxiliary valve seat 13 form sealing to cut off the medium auxiliary flow passage 12, the inlet medium stops entering the piston cavity 16, meanwhile, the residual medium in the piston cavity 16 is discharged to an outlet through a small flow limiting hole 15 in the throttling nail 8 and an elongated hole 17 (inner hole flow passage) in the main valve core 6, the medium pressure in the piston cavity 16 rapidly drops, an opening pressure difference in the closing direction (leftwards in the current figure) is formed on the main valve core 6, the main valve core 6 is driven to move leftwards to be closed, the closing sealing is kept to be closed under.
The implementation example of applying the invention to a certain pre-researched model quick-response high-performance attitude control engine is as follows:
the quick response on-off control requirements of propellant media with the flow of 0.8Kg/s and the working pressure of 13MPa are provided for a 3000N engine control valve, the response requirements of opening and closing are not more than 15ms, and meanwhile, the compact structure and the small size and light weight are ensured. The control valve is adopted during development, and through production tests of multiple batches of products and test run and examination of engines, the control valve is quick in opening and closing response, reliable in sealing and action and light in structural weight, and achieves the design target.
Claims (3)
1. Axial-flow type electromagnetic pilot pressure difference drive large-flow control valve is characterized in that: the electromagnetic auxiliary valve and the differential pressure main valve are integrated into a whole along the axial direction;
the electromagnetic auxiliary valve comprises an auxiliary valve body (2), an electromagnetic coil (3), an auxiliary valve core (4), an auxiliary return spring (5) and an auxiliary valve seat (13);
the differential pressure main valve comprises a main valve body (1), a main valve core (6), a main return spring (7), a main valve seat (14) and a retainer (10);
an inlet nozzle is integrated on the auxiliary valve body (2) and is used as an inlet of the control valve; the auxiliary valve core (4) is arranged in the auxiliary valve body (2); the electromagnetic coil (3) is sleeved outside the auxiliary valve core (4) and is positioned between the auxiliary valve body (2) and the auxiliary valve core (4); one end of the return auxiliary spring (5) is connected/contacted with the auxiliary valve body (2), and the other end is connected/contacted with one end of the auxiliary valve core (4); the auxiliary valve seat (13) is integrated in the main valve body (1) and is positioned on the central axis of the main valve body (1);
an outlet connecting nozzle is integrated on the main valve body (1) and is used as a control valve outlet; the main valve core (6), the reset main spring (7) and the retainer (10) are sequentially arranged in the main valve body (1) along the axial direction, and the main valve core (6) is closer to the electromagnetic auxiliary valve; one end of the main valve core (6) close to the electromagnetic auxiliary valve is a piston section, and the other end of the main valve core is a sealing section; the outer wall of the piston section of the main valve core (6) is matched with the inner wall of the main valve body (1) in a guiding way, and a piston cavity (16) is formed; the main valve seat (14) is integrated on the inner wall of the main valve core (6) close to the outlet nozzle;
a first medium flow channel hole (20) is arranged on the auxiliary valve core (4), and a second medium flow channel hole (21) is arranged on the side wall of the main valve body (1); one end of the first medium flow channel hole (20) is communicated with the inlet filler head, and the other end of the first medium flow channel hole (21) is communicated with the second medium flow channel hole (21); the first medium flow channel hole (20) and the second medium flow channel hole (21) form a large-diameter main flow channel (11) of the control valve; the main valve seat (14) and the main valve core (6) form a switch sealing pair of a medium main flow passage (11);
an auxiliary flow passage hole (22) is arranged at the central shaft position of the main valve body (1), and the auxiliary flow passage hole (22) axially penetrates through the auxiliary valve seat (13) and is communicated with the piston cavity (16); a throttling nail (8) with a small throttling hole (15) and an elongated hole (17) are sequentially arranged on the central shaft of the main valve core (6); one end of the elongated hole (17) is communicated with the piston cavity (16) through the small restricted hole (15), and the other end is communicated with the outlet nozzle; the elongated hole (17), the small flow limiting hole (15) and the secondary flow passage hole (22) jointly form a secondary flow passage (12) of the control valve, and the secondary valve seat (13) and the secondary valve core (4) form a switching sealing pair of the secondary flow passage (12).
2. The axial flow type electromagnetic pilot differential pressure driven large flow control valve according to claim 1, characterized in that: the diameter of the piston section of the main valve core (6) is larger than the sealing diameter of the main valve seat of the main valve core.
3. The axial flow type electromagnetic pilot differential pressure driven large flow control valve according to claim 2, characterized in that: the aperture of a small flow limiting hole (15) on the throttling nail (8) is designed in a matching mode according to parameters of the drift diameter of the auxiliary valve seat (13), the diameter of the piston section of the main valve core (6), the volume of the piston cavity (16) and the sealing diameter of the main valve core seat.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011301866.8A CN112324975A (en) | 2020-11-19 | 2020-11-19 | Axial-flow type electromagnetic pilot pressure difference driving large-flow control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011301866.8A CN112324975A (en) | 2020-11-19 | 2020-11-19 | Axial-flow type electromagnetic pilot pressure difference driving large-flow control valve |
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| Publication Number | Publication Date |
|---|---|
| CN112324975A true CN112324975A (en) | 2021-02-05 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011301866.8A Pending CN112324975A (en) | 2020-11-19 | 2020-11-19 | Axial-flow type electromagnetic pilot pressure difference driving large-flow control valve |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5529387A (en) * | 1994-09-06 | 1996-06-25 | Valcor Engineering Corporation | Solenoid operated discharging orifice shutoff valve |
| GB2417546A (en) * | 2004-08-30 | 2006-03-01 | Schlumberger Holdings | Pilot Valve |
| CN102506208A (en) * | 2011-12-19 | 2012-06-20 | 铜陵市三圆特种铸造有限责任公司 | Gas electromagnetic valve |
| JP2014062579A (en) * | 2012-09-20 | 2014-04-10 | Saginomiya Seisakusho Inc | Control valve |
| CN105570470A (en) * | 2015-12-20 | 2016-05-11 | 西安航天动力研究所 | Built-in pilot operated solenoid valve |
| CN110259954A (en) * | 2019-06-14 | 2019-09-20 | 西安航天动力研究所 | Integrated direct-acting electromagnetic valve |
-
2020
- 2020-11-19 CN CN202011301866.8A patent/CN112324975A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5529387A (en) * | 1994-09-06 | 1996-06-25 | Valcor Engineering Corporation | Solenoid operated discharging orifice shutoff valve |
| GB2417546A (en) * | 2004-08-30 | 2006-03-01 | Schlumberger Holdings | Pilot Valve |
| CN102506208A (en) * | 2011-12-19 | 2012-06-20 | 铜陵市三圆特种铸造有限责任公司 | Gas electromagnetic valve |
| JP2014062579A (en) * | 2012-09-20 | 2014-04-10 | Saginomiya Seisakusho Inc | Control valve |
| CN105570470A (en) * | 2015-12-20 | 2016-05-11 | 西安航天动力研究所 | Built-in pilot operated solenoid valve |
| CN110259954A (en) * | 2019-06-14 | 2019-09-20 | 西安航天动力研究所 | Integrated direct-acting electromagnetic valve |
Non-Patent Citations (1)
| Title |
|---|
| "三结合"编写小组: "《液压技术》", 31 December 1972, 广州机床研究所 * |
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Application publication date: 20210205 |
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