A high pressure electrically controlled valve and pressurized delivery device

Abstract

The application is suitable for the technical field of aerospace valves, and provides a high-pressure electric control valve, which comprises a valve assembly and a driving mechanism, the valve assembly comprises a valve rod and a valve body with a containing cavity, and the valve body is provided with an inlet and an outlet; the valve rod is provided with a first sealing protrusion and a second sealing protrusion along the circumferential side wall, and the diameter of the first sealing protrusion is smaller than that of the second sealing protrusion; the driving mechanism comprises a fixed sleeve, a piston, a first control valve and hydraulic oil, the fixed sleeve is provided with a separation part, the separation part separates the fixed sleeve into a first inner cavity and a second inner cavity, and the separation part is provided with a penetrating hole for the valve rod to pass through and be fixedly connected with the piston; the first control valve is used for connecting or disconnecting the first inner cavity and the second inner cavity. In the application, the high-pressure electric control valve is opened or closed smoothly, the water hammer phenomenon caused to the pressure boosting conveying device is avoided, the use of a detonator in the high-pressure electric control valve is avoided, the application has the properties of repeated work and test, and the manufacturing cost and use cost are reduced.

Description

Technical Field

[0001] This invention belongs to the field of aerospace valve technology, and particularly relates to a high-pressure electrically controlled valve and a booster delivery device. Background Technology

[0002] High-pressure control valves are widely used in the pressurization and delivery systems of liquid propellant rockets. Their main function is to isolate the high-pressure gas or liquid in the propulsion system from downstream pressure reducing valves, solenoid valves and other components before the launch of the liquid propellant rocket. During operation, they send an electrical signal to open the high-pressure control valve, connecting the pressurization and delivery system to the storage tank. This provides protection and isolation, and improves the reliability and storage performance of the liquid propellant rocket.

[0003] Existing high-pressure control valves utilize electro-explosive valves. These valves, activated by pyrotechnic devices such as electro-explosive tubes within the valve, generate high-pressure gas that drives an actuating mechanism to open or close the flow path. Based on their working principle, they can be categorized into normally closed and normally open electro-explosive valves. However, in pressurization and delivery systems using electro-explosive valves as high-pressure control valves, the presence of pyrotechnic devices presents significant challenges. The development and management of these devices are extremely demanding, requiring specialized facilities and equipment for assembly and testing. Furthermore, electro-explosive valves are single-use and lack the capability for repeated operation and testing, increasing manufacturing and operating costs. During operation, the impact of pyrotechnic ignition is substantial, easily generating excess fragments or debris that can disrupt the normal operation of the pressurization and delivery system. Additionally, the rapid opening and closing speed of electro-explosive valves can easily cause water hammer within the pressurization and delivery system, thereby affecting the reliability of liquid-fueled rockets. Summary of the Invention

[0004] The purpose of this invention is to provide a high-pressure electrically controlled valve, which aims to solve the technical problems of existing electric explosion valves, which contain pyrotechnic components. These valves require specialized sites and equipment for assembly and testing, and lack the ability to perform repetitive work and testing, thus increasing their manufacturing and operating costs. Furthermore, electric explosion valves generate significant impacts during operation, easily producing excess fragments or debris that affect the normal operation of the pressurization and delivery system. Additionally, the rapid opening and closing speed of electric explosion valves can easily cause water hammer in the pressurization and delivery system, thereby affecting the reliability of liquid-fueled rockets.

[0005] To achieve the above objectives, the technical solution adopted by the present invention is: to provide a high-pressure electrically controlled valve for a pressurization and delivery device for a liquid launch vehicle, comprising:

[0006] A valve assembly includes a valve stem and a valve body having a receiving cavity. The valve body has a clearance hole at its end for the valve stem to enter the receiving cavity. The valve body has an inlet and an outlet communicating with the receiving cavity and the outside, respectively, and the inlet and outlet are offset from each other. The valve stem has a first sealing protrusion and a second sealing protrusion protruding along its circumferential sidewall to isolate or connect the inlet and the outlet. The first sealing protrusion and the second sealing protrusion are spaced apart, and the diameter of the first sealing protrusion is smaller than the diameter of the second sealing protrusion.

[0007] The drive mechanism includes a fixed sleeve fixedly connected to the valve body, a piston, a first control valve, and hydraulic oil. The fixed sleeve has a partition that divides the interior of the fixed sleeve into a first inner cavity for inserting the valve stem and a second inner cavity for inserting the piston. The partition has a through hole through which the valve stem passes and is fixedly connected to the piston. The fixed sleeve is equipped with the first control valve, which is used to connect or disconnect the first inner cavity and the second inner cavity.

[0008] The second sealing protrusion, the partition, and the circumferential inner wall of the fixed sleeve form a first temporary storage area for temporarily storing the hydraulic oil. The piston, the partition, and the circumferential inner wall of the fixed sleeve form a second temporary storage area for temporarily storing the hydraulic oil. When the hydraulic oil is temporarily stored in the first temporary storage area, the inlet and the outlet are in a connected state. When the hydraulic oil is temporarily stored in the second temporary storage area, the inlet and the outlet are in a separated state.

[0009] In one embodiment, the high-pressure electrically controlled valve further includes a position sensor disposed on the valve body. The valve stem has a third sealing protrusion protruding along its circumferential sidewall. The third sealing protrusion and the second sealing protrusion are spaced apart. The third sealing protrusion is disposed on the opposite side of the second sealing protrusion facing the first sealing protrusion. A first boss, a second boss, and a third boss are sequentially connected on the outer surface of the valve stem located between the second sealing protrusion and the third sealing protrusion. The elastic contact of the position sensor is in movable contact with the first boss, the second boss, and the third boss.

[0010] In one embodiment, the valve stem is provided with a connecting part that is fixedly connected to the piston, and the surfaces of the connecting part, the first sealing protrusion, the second sealing protrusion, the third sealing protrusion, and the piston are all provided with sealing grooves for installing sealing rings.

[0011] In one embodiment, the valve stem has a fourth sealing protrusion protruding along its circumferential sidewall. The fourth sealing protrusion and the first sealing protrusion are spaced apart. The fourth sealing protrusion is located on the opposite side of the first sealing protrusion facing the second sealing protrusion. The diameters of the first sealing protrusion and the fourth sealing protrusion are equal. When the hydraulic oil is temporarily stored in the first temporary storage area, the inlet and the outlet are isolated. When the hydraulic oil is temporarily stored in the second temporary storage area, the inlet and the outlet are connected.

[0012] In one embodiment, the end of the fixed sleeve is provided with a limiting block for restricting the movement of the piston.

[0013] In one embodiment, the high-pressure electrically controlled valve further includes an adjusting nut threadedly connected to the end of the fixed sleeve, for driving the piston to move relative to the fixed sleeve in the second inner cavity, and the outer surface of the fixed sleeve is provided with a scale for measuring the movement distance of the adjusting nut.

[0014] In one embodiment, a second control valve is provided on the partition, the second control valve being used to connect or disconnect the first inner cavity and the second inner cavity.

[0015] In one embodiment, the first control valve is a solenoid valve, and the second control valve is a solenoid valve or a check valve.

[0016] In one embodiment, the outer surface of the valve body is provided with a mounting structure.

[0017] The purpose of this invention is to provide a pressurization and delivery device, which aims to solve the technical problems of existing pressurization and delivery systems using electro-explosive valves. These valves contain pyrotechnic components, requiring specialized sites and equipment for assembly and testing. They also lack the ability to perform repetitive work and testing, increasing manufacturing and operating costs. Furthermore, the electro-explosive valves generate significant impacts during operation, easily producing excess debris or impurities that affect the normal operation of the pressurization and delivery system. Additionally, the rapid opening and closing speed of the electro-explosive valves can easily cause water hammer in the pressurization and delivery system, thereby affecting the reliability of liquid-fueled rockets.

[0018] To achieve the above objectives, the technical solution adopted by the present invention is to provide a pressurization and delivery device for liquid launch vehicles, including the high-pressure electrically controlled valve as described above.

[0019] The beneficial effects of the high-pressure electrically controlled valve provided by this invention are as follows: Compared with existing high-pressure electrically controlled valves, the high-pressure electrically controlled valve of this invention is used in the pressurization and delivery device of a liquid launch vehicle. The high-pressure electrically controlled valve includes a valve assembly and a drive mechanism. The opening or closing of the first control valve of the drive mechanism is controlled by an electrical signal, so that the valve stem of the control valve stem assembly slides axially relative to the valve body within the accommodating cavity of the valve body. This enables the connection or isolation of the inlet and outlet on the control valve body, thereby achieving remote cutoff or conduction of the high-pressure fluid medium in the pressurization and delivery device of the liquid launch vehicle. Because the opening or closing of the high-pressure electrically controlled valve is relatively smooth, it avoids large impacts during operation, preventing water hammer from occurring on the pressurization and delivery device. It also avoids the generation of excess debris that could affect the normal operation of the pressurization and delivery system due to excessive impacts during use. At the same time, by avoiding the use of pyrotechnics in the high-pressure electrically controlled valve, the hardware requirements such as the site and equipment required for its assembly and testing are reduced. It also has the attribute of repetitive work and testing, effectively reducing the manufacturing and usage costs of the high-pressure electrically controlled valve, which is conducive to improving the reliability of the liquid launch vehicle. Attached Figure Description

[0020] Figure 1 This is a cross-sectional view of a high-pressure electrically controlled valve in the open state according to an embodiment of the present invention;

[0021] Figure 2 This is a cross-sectional view of a high-pressure electrically controlled valve in the closed state according to an embodiment of the present invention;

[0022] Figure 3 This is a cross-sectional view of a high-pressure electrically controlled valve in the closed state according to another embodiment of the present invention;

[0023] Figure 4 This is a cross-sectional view of a high-pressure electrically controlled valve in the open state, according to another embodiment of the present invention.

[0024] Figure 5 This is a three-dimensional structural diagram of the valve body of a high-pressure electrically controlled valve provided in one embodiment of the present invention;

[0025] Figure 6 This is a cross-sectional view of the valve body of a high-pressure electrically controlled valve provided in one embodiment of the present invention;

[0026] Figure 7 This is a partial cross-sectional view of a high-pressure electrically controlled valve in the closed state, according to another embodiment of the present invention.

[0027] Figure 8 This is a cross-sectional view of the valve stem of a high-pressure electrically controlled valve provided in another embodiment of the present invention;

[0028] Figure 9This is a cross-sectional view of the fixing sleeve of a high-pressure electrically controlled valve provided in one embodiment of the present invention;

[0029] The following are the labeling elements in the figure:

[0030] 1. High-pressure electrically controlled valve; 2. Valve assembly; 21. Valve stem; 211. Connecting part; 212. First sealing protrusion; 213. Second sealing protrusion; 214. Third sealing protrusion; 215. Fourth sealing protrusion; 216. First boss; 217. Second boss; 218. Third boss; 22. Valve body; 221. Receiving cavity; 222. Displacement hole; 223. Feed inlet; 224. Discharge outlet; 225. Mounting structure; 3. Drive mechanism; 31. Fixed sleeve; 311. Separator; 3111. Through hole; 312. First inner cavity; 313. Second inner cavity; 314. First temporary storage area; 315. Second temporary storage area; 32. Piston; 33. First control valve; 34. Second control valve; 35. Hydraulic oil; 36. Limit block; 37. Adjusting nut; 4. Position sensor; 5. Sealing ring. Detailed Implementation

[0031] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the invention.

[0032] The high-pressure electrically controlled valve 1 of the present invention is used in the pressurization and delivery device of a liquid launch vehicle. The high-pressure electrically controlled valve 1 includes a valve assembly 2 and a drive mechanism 3. The first control valve 33 of the drive mechanism 3 is opened or closed via an electrical signal, thereby controlling the valve stem 21 of the control valve stem 21 assembly to slide axially relative to the valve body 22 within the accommodating cavity 221 of the valve body 22. This enables the connection or isolation of the inlet 223 and outlet 224 on the control valve body 22, thereby achieving remote control of the high-pressure fluid medium in the pressurization and delivery device of the liquid launch vehicle. The opening and closing of the high-pressure electrically controlled valve 1 is relatively smooth, avoiding large impacts during operation and preventing water hammer on the pressurization and delivery device. It can also prevent excessive debris from being generated during use, which would affect the normal operation of the pressurization and delivery system. At the same time, by avoiding the use of pyrotechnics in the high-pressure electrically controlled valve 1, the hardware requirements such as the site and equipment required for its assembly and testing are reduced, and it has the attribute of repetitive work and testing, which effectively reduces the manufacturing cost and operating cost of the high-pressure electrically controlled valve 1, and is conducive to improving the reliability of liquid launch vehicles.

[0033] Example 1

[0034] Please refer to the following: Figure 1 , Figure 2 , Figure 5 , Figure 6 and Figure 9 The high-pressure electrically controlled valve 1 of the present invention is used in a pressurization and delivery device for a liquid launch vehicle, comprising:

[0035] Valve assembly 2 includes a valve stem 21 and a valve body 22 having a receiving cavity 221. The valve body 22 has a clearance hole 222 at its end for the valve stem 21 to be inserted into the receiving cavity 221. The valve body 22 has an inlet 223 and an outlet 224 that connect the receiving cavity 221 to the outside. The inlet 223 and the outlet 224 are staggered. The valve stem 21 has a first sealing protrusion 212 and a second sealing protrusion 213 protruding along its circumferential sidewall to isolate or connect the inlet 223 and the outlet 224. The first sealing protrusion 212 and the second sealing protrusion 213 are spaced apart. The diameter of the first sealing protrusion 212 is smaller than the diameter of the second sealing protrusion 213.

[0036] The drive mechanism 3 includes a fixed sleeve 31 fixedly connected to the valve body 22, a piston 32, a first control valve 33, and hydraulic oil 35. The fixed sleeve 31 is provided with a partition 311, which divides the fixed sleeve 31 into a first inner cavity 312 for inserting the valve rod 21 and a second inner cavity 313 for inserting the piston 32. The partition 311 is provided with a through hole 3111 for the valve rod 21 to pass through and be fixedly connected to the piston 32. The fixed sleeve 31 is provided with the first control valve 33, which is used to connect or disconnect the first inner cavity 312 and the second inner cavity 313.

[0037] The second sealing protrusion 213, the partition 311, and the circumferential inner wall of the fixed sleeve 31 enclose a first temporary storage area 314 for temporarily storing hydraulic oil 35. The piston 32, the partition 311, and the circumferential inner wall of the fixed sleeve 31 enclose a second temporary storage area 315 for temporarily storing hydraulic oil 35. When the hydraulic oil 35 is temporarily stored in the first temporary storage area 314, the inlet 223 and the outlet 224 are in a connected state. When the hydraulic oil 35 is temporarily stored in the second temporary storage area 315, the inlet 223 and the outlet 224 are in a separated state.

[0038] The connection method between the fixed sleeve 31 of the drive mechanism 3 and the valve body 22 of the valve assembly 2 is not limited here. It can be a detachable connection or a non-detachable connection. Preferably, the fixed sleeve 31 and the valve body 22 are fixedly connected by screws, which facilitates assembly and disassembly and makes it easier for operators to carry out maintenance.

[0039] Please refer to further information. Figure 1 and Figure 2In this embodiment, the inlet 223 and outlet 224 on the valve body 22 of the high-pressure solenoid valve 1 are misaligned and connected to the pressurization and delivery system of the liquid launch vehicle. The high-pressure fluid medium flows in from the inlet 223 and flows out from the outlet 224 of the valve body 22. One end of the valve stem 21 of the valve assembly 2 passes through the relief hole 222 of the valve body 22 and is inserted into the receiving cavity 221, while the other end passes through the through hole 3111 on the partition 311 and is fixedly connected to the piston 32. Since the first sealing protrusion 212 and the second sealing protrusion 213 on the valve stem 21 are spaced apart, the high-pressure fluid medium flows between the first sealing protrusion 212 and the second sealing protrusion 213. The diameter of the first sealing protrusion 212 is smaller than the diameter of the second sealing protrusion 213, resulting in the force-bearing area of ​​the end face of the first sealing protrusion 212 being smaller than the force-bearing area of ​​the end face of the second sealing protrusion 213. The accumulation of fluid causes the valve stem 21 to be subjected to an axial force that squeezes the piston 32 when the high-pressure fluid medium flows through it. However, since the hydraulic oil 35 is temporarily stored in the first temporary storage area 314 and is incompressible, the first control valve 33 disconnects the connection between the first inner cavity 312 and the second inner cavity 313, preventing the hydraulic oil 35 from flowing into the second temporary storage area 315. This restricts the axial sliding of the valve stem 21 relative to the valve body 22, thereby keeping the inlet 223 and the outlet 224 connected and the high-pressure solenoid valve 1 open. In other words, the high-pressure solenoid valve 1 is a normally open solenoid valve.

[0040] When the high-pressure solenoid valve 1 needs to be closed, the first control valve 33 of the drive mechanism 3 is opened by an electrical signal, connecting the first inner cavity 312 and the second inner cavity 313. The valve stem 21 is subjected to the force of the high-pressure fluid medium applied to the end face of the second sealing protrusion 213, and slides relative to the valve body 22 in the direction closer to the partition 311. The end face of the second sealing protrusion 213 squeezes the hydraulic oil 35 from the first temporary storage area 314 through the first control valve 33 and into the second temporary storage area 315. At the same time, the piston 32 is pushed by the valve stem 21 and slides relative to the fixed sleeve 31 in the direction away from the partition 311 until the end face of the second sealing protrusion 213 abuts against the surface of the partition 311 and is limited. At this time, the first sealing protrusion 212 and the inner wall of the valve body 22 form a sealing structure, disconnecting the connection between the inlet 223 and the outlet 224, so that the high-pressure fluid medium cannot flow to the outlet 224 after entering the inlet 223.

[0041] When the high-pressure solenoid valve 1 needs to be reopened, the operator applies external force to the piston 32, causing it to slide relative to the fixed sleeve 31 towards the direction closer to the partition 311. Since the valve stem 21 is fixedly connected to the piston 32, the piston 32 transmits power to the valve stem 21, causing the valve stem 21 to overcome the force exerted by the high-pressure fluid medium on the end face of the second sealing protrusion 213 under the action of external force, and slide relative to the valve body 22 towards the direction away from the partition 311 until the end face of the piston 32 abuts against the surface of the partition 311 and is limited. At the same time, the end face of the piston 32 squeezes the hydraulic oil 35 from the second temporary storage area 315 through the first control valve 33 and into the first temporary storage area 314. At this time, the inlet 223 and the outlet 224 are in a connected state. In the first stage, the high-pressure fluid medium flows into the valve body 22 from the inlet 223, flows between the first sealing protrusion 212 and the second sealing protrusion 213, and flows out of the valve body 22 from the outlet 224. The first control valve 33 of the drive mechanism 3 is closed by controlling the electrical signal to disconnect the connection between the first inner cavity 312 and the second inner cavity 313, so that the hydraulic oil 35 is temporarily stored in the first temporary storage area 314, thereby restricting the axial sliding of the valve stem 21 relative to the valve body 22. This keeps the inlet 223 and the outlet 224 connected, and the high-pressure solenoid valve 1 remains open, giving the high-pressure solenoid valve 1 the attribute of repeated operation and testing. This effectively reduces the manufacturing cost and usage cost of the high-pressure solenoid valve 1 and helps to improve the reliability of the liquid launch vehicle.

[0042] As the hydraulic oil 35 flows through the first control valve 33, its flow rate is limited by the orifice diameter of the first control valve 33. This results in the high-pressure solenoid valve 1 opening or closing more smoothly, avoiding large impacts during operation and preventing water hammer on the booster conveying device. It also prevents excessive debris from affecting the normal operation of the booster conveying system due to excessive impacts during use.

[0043] Example 2

[0044] Please refer to further information. Figures 3 to 9In this embodiment, the valve stem 21 of the high-pressure solenoid valve 1 has a fourth sealing protrusion 215 protruding along the circumferential sidewall. The fourth sealing protrusion 215 and the first sealing protrusion 212 are spaced apart. The fourth sealing protrusion 215 is located on the opposite side of the first sealing protrusion 212 facing the second sealing protrusion 213. The diameter of the first sealing protrusion 212 and the diameter of the fourth sealing protrusion 215 are equal. When the hydraulic oil 35 is temporarily stored in the first temporary storage area 314, the inlet 223 and the outlet 224 are isolated. When the hydraulic oil 35 is temporarily stored in the second temporary storage area 315, the inlet 223 and the outlet 224 are connected. Since the first sealing protrusion 212, the second sealing protrusion 213 and the fourth sealing protrusion 215 on the valve stem 21 are arranged side by side and spaced apart, the first sealing protrusion 212 and the fourth sealing protrusion 215 on the valve stem 21 and the inner wall of the valve body 22 form a sealing structure, which disconnects the connection between the feed port 223 and the discharge port 224, so that the initial state of the high-pressure solenoid valve 1 is the closed state. High-pressure fluid medium flows into the inlet 223 and flows between the first sealing protrusion 212 and the second sealing protrusion 213. The diameter of the first sealing protrusion 212 is smaller than that of the second sealing protrusion 213, resulting in the force-bearing area of ​​the end face of the first sealing protrusion 212 being smaller than that of the end face of the second sealing protrusion 213. As a result, when the high-pressure fluid medium flows through the valve stem 21, the valve stem 21 is subjected to an axial force that squeezes towards the piston 32. However, since the hydraulic oil 35 is temporarily stored in the first temporary storage area 314 at this time, and the hydraulic oil 35 is incompressible, the first control valve 33 disconnects the connection between the first inner cavity 312 and the second inner cavity 313, causing the hydraulic oil 35 to be unable to flow into the second temporary storage area 315. This restricts the axial sliding of the valve stem 21 relative to the valve body 22, thereby keeping the inlet 223 and the outlet 224 in a disconnected state, and the high-pressure solenoid valve 1 in a closed state. That is, the high-pressure solenoid valve 1 is a normally closed solenoid valve.

[0045] When the high-pressure solenoid valve 1 needs to be opened, the first control valve 33 of the drive mechanism 3 is opened by an electrical signal, connecting the first inner cavity 312 and the second inner cavity 313; the valve stem 21 is subjected to the force of the high-pressure fluid medium applied to the end face of the second sealing protrusion 213, and slides relative to the valve body 22 in the direction closer to the partition 311. The end face of the second sealing protrusion 213 squeezes the hydraulic oil 35 from the first temporary storage area 314 through the first control valve 33 and into the second temporary storage area 315; at the same time, the piston 32 slides relative to the fixed sleeve 31 in the direction away from the partition 311 under the thrust of the valve stem 21. Since the diameters of the first sealing protrusion 212 and the fourth sealing protrusion 215 are equal, when the valve stem 21 slides to the point where the high-pressure fluid medium flows between the first sealing protrusion 212 and the fourth sealing protrusion 215, the end faces of the first sealing protrusion 212 and the fourth sealing protrusion 215 reach a force balance, causing the valve stem 21 to stop sliding. At this time, the inlet 223 and the outlet 224 are in a connected state, and the high-pressure fluid medium flows into the valve body 22 from the inlet 223, flows between the first sealing protrusion 212 and the fourth sealing protrusion 215, and flows out of the valve body 22 from the outlet 224.

[0046] When the high-pressure solenoid valve 1 needs to be closed again, the operator applies external force to the piston 32, causing it to slide relative to the fixed sleeve 31 towards the direction closer to the partition 311. Since the valve stem 21 is fixedly connected to the piston 32, the piston 32 transmits power to the valve stem 21, causing the valve stem 21 to overcome the force exerted by the high-pressure fluid medium on the end face of the second sealing protrusion 213 under the action of external force, and slide relative to the valve body 22 towards the direction away from the partition 311 until the end face of the piston 32 abuts against the surface of the partition 311 and is limited. At the same time, the end face of the piston 32 squeezes the hydraulic oil 35 from the second temporary storage area 315 through the first control valve 33 and into the first temporary storage area 314. At this time, the first sealing protrusion 212 and the fourth sealing protrusion 215 on the valve stem 21 and the inner wall of the valve body 22 form a sealing structure, disconnecting the connection between the inlet 223 and the outlet 224, so that the high-pressure fluid medium cannot flow to the outlet 224 after entering the inlet 223. Simultaneously, the first control valve 33 of the drive mechanism 3 is closed by controlling the electrical signal, disconnecting the connection between the first inner cavity 312 and the second inner cavity 313, so that the hydraulic oil 35 is temporarily stored in the first temporary storage area 314, thereby restricting the axial sliding of the valve stem 21 relative to the valve body 22, thereby keeping the inlet 223 and outlet 224 in a disconnected state, and keeping the high-pressure solenoid valve 1 in a closed state, so that the high-pressure solenoid valve 1 has the attribute of repeated work and testing, effectively reducing the manufacturing cost and usage cost of the high-pressure solenoid valve 1, which is conducive to improving the reliability of liquid launch vehicles.

[0047] Example 3

[0048] Please refer to the following: Figures 3 to 8In this embodiment, the high-pressure solenoid valve 1 further includes a position sensor 4 disposed on the valve body 22. A third sealing protrusion 214 is formed by protruding along the circumferential sidewall of the valve stem 21. The third sealing protrusion 214 and the second sealing protrusion 213 are spaced apart. The third sealing protrusion 214 is disposed on the opposite side of the second sealing protrusion 213 facing the first sealing protrusion 212. A first boss 216, a second boss 217 and a third boss 218 are sequentially connected on the outer surface of the valve stem 21 located between the second sealing protrusion 213 and the third sealing protrusion 214. The elastic contact of the position sensor 4 is in movable contact with the first boss 216, the second boss 217 and the third boss 218. The working state of the high-pressure solenoid valve 1 is determined by the electrical signal fed back by the elastic contact of the position sensor 4.

[0049] When the high-pressure solenoid valve 1 is a normally open solenoid valve, the elastic contact of the position sensor 4 is in a closed state when it abuts against the first boss 216, in a working state when it abuts against the second boss 217, and in an open state when it abuts against the third boss 218; when the high-pressure solenoid valve 1 is a normally closed solenoid valve, the elastic contact of the position sensor 4 is in an open state when it abuts against the first boss 216, in a working state when it abuts against the second boss 217, and in a closed state when it abuts against the third boss 218.

[0050] Optionally, the connection between the first boss 216 and the second boss 217, as well as the connection between the second boss 217 and the third boss 218, are all set with slopes, which helps the elastic contact of the position sensor 4 to slide on its surface without getting stuck, and also helps to extend the service life of the position sensor 4.

[0051] Example 4

[0052] Please see Figure 7 In this embodiment, the valve stem 21 of the high-pressure solenoid valve 1 is provided with a connecting part 211 that is fixedly connected to the piston 32. The connecting part 211 passes through the through hole 3111 on the partition 311 and is fixedly connected to the piston 32. The connection method between the connecting part 211 and the piston 32 is not limited here, and a detachable connection or a non-detachable connection can be used. Preferably, the outer surface of the connecting part 211 is provided with an external thread, and the end face of the piston 32 is recessed inward to form a connecting hole for the connecting part 211 to be inserted. The inner sidewall of the connecting hole is provided with an internal thread that matches the external thread. The valve stem 21 and the piston 32 are fixedly connected by a threaded connection, which facilitates assembly and disassembly.

[0053] Optionally, sealing grooves for installing sealing rings 5 ​​are provided on the surfaces of the connecting part 211, the first sealing protrusion 212, the second sealing protrusion 213, the third sealing protrusion 214, the fourth sealing protrusion 215, and the piston 32. By providing sealing grooves on the surfaces of the first sealing protrusion 212, the second sealing protrusion 213, and the fourth sealing protrusion 215, and placing sealing rings 5 ​​within these grooves, the gap between the valve stem 21 and the valve body 22 is sealed, thereby preventing the high-pressure fluid medium from overflowing into the preset flow path, which helps to ensure the operation of the high-pressure solenoid valve 1. The stability and reliability of the process are ensured by providing sealing grooves on the surface of the third sealing protrusion 214, the surface of the connecting part 211, and the surface of the piston 32, and providing sealing rings 5 ​​in the sealing grooves to seal the gap between the valve stem 21 and the fixed sleeve 31, and the gap between the piston 32 and the fixed sleeve 31. This prevents hydraulic oil 35 from leaking from the first temporary storage area 314 or the second temporary storage area 315, and prevents the high-pressure solenoid valve 1 from being affected by insufficient storage of hydraulic oil 35, thus ensuring the stability and reliability of the high-pressure solenoid valve 1 structure and extending the service life of the high-pressure solenoid valve 1.

[0054] Example 5

[0055] Please refer to the following: Figures 1 to 4 In this embodiment, a limiting block 36 is provided at the end of the fixed sleeve 31 of the high-pressure solenoid valve 1 to restrict the movement of the piston 32. The limiting block 36 restricts the axial movement of the piston 32 relative to the fixed sleeve 31, preventing accidental operation by the operator that could cause the first control valve 33 to open and thus change the state of the high-pressure solenoid valve 1, thereby improving the reliability of the high-pressure solenoid valve 1. When the high-pressure solenoid valve 1 needs to be operated and its state changed, the limiting block 36 must first be removed from the fixed sleeve 31.

[0056] Optionally, the high-pressure solenoid valve 1 also includes an adjusting nut 37 threadedly connected to the end of the fixed sleeve 31, used to drive the piston 32 to move relative to the fixed sleeve 31 in the second inner cavity 313. When the piston 32 is in a position away from the partition 311 and needs to move relative to the fixed sleeve 31 in a direction closer to the partition 311, the limiting block 36 is first installed on the fixed sleeve 31, and then the adjusting nut 37 is sleeved on the end of the fixed sleeve 31. The operator can then turn the adjusting nut 37 to drive the piston 32 to move relative to the fixed sleeve 31, thereby changing the state of the high-pressure solenoid valve 1.

[0057] Optionally, the outer surface of the fixed sleeve 31 is provided with a scale for measuring the movement distance of the adjusting nut 37, so that the operator can intuitively obtain the movement distance of the piston 32.

[0058] Example 6

[0059] Please refer to the following: Figure 3 , Figure 4 and Figure 9 In this embodiment, a second control valve 34 is provided on the partition portion 311 of the fixed sleeve 31. The second control valve 34 is used to connect or disconnect the first inner cavity 312 and the second inner cavity 313. When the hydraulic oil 35 flows from the first temporary storage area 314 to the second temporary storage area 315, the first control valve 33 is opened and the second control valve 34 is kept closed. When the hydraulic oil 35 flows from the second temporary storage area 315 to the first temporary storage area 314, the second control valve 34 is opened and the first control valve 33 is kept closed.

[0060] Optionally, the first control valve 33 is a pilot solenoid valve, and the second control valve 34 is a pilot solenoid valve or a check valve. When both the first control valve 33 and the second control valve 34 are pilot solenoid valves, the operator controls the opening or closing of the first control valve 33 and the second control valve 34 through an electrical signal. When the first control valve 33 is a pilot solenoid valve and the second control valve 34 is a check valve, the operator controls the opening or closing of the first control valve 33 through an electrical signal, and the second control valve 34 can be controlled to open or close by the pressure applied to the second control valve 34 by the hydraulic oil 35.

[0061] Example 7

[0062] Please refer to further information. Figure 3 , Figure 4 and Figure 6 In this embodiment, the valve body 22 has a first vent hole on the end face opposite to the end with the clearance hole 222, which connects the accommodating cavity 221 to the outside. The valve body 22 has a second vent hole on the side wall at the corresponding position between the second sealing protrusion 213 and the third sealing protrusion 214 of the valve stem 21, which connects the accommodating cavity 221 to the outside. The first vent hole and the second vent hole can timely discharge excess gas in the accommodating cavity 221, or draw in an appropriate amount of gas from the outside into the accommodating cavity 221, to ensure that the air pressure in the accommodating cavity 221 is the same as the atmospheric pressure. This avoids the high pressure solenoid valve 1 from being affected by the air pressure in the accommodating cavity 221 of the valve body 22 being too high or too low, thus helping to ensure the stability and reliability of the high pressure solenoid valve 1.

[0063] Example 8

[0064] Please refer to the following: Figures 5 to 6In this embodiment, the outer surface of the valve body 22 of the high-pressure solenoid valve 1 is provided with a mounting structure 225, which facilitates the installation of the high-pressure solenoid valve 1 on the booster conveying device. Optionally, there are multiple mounting structures 225 on the valve body 22, and the multiple mounting structures 225 are evenly distributed around the circumference of the valve body 22, which helps to more stably install the high-pressure solenoid valve 1 on the booster conveying device.

[0065] Example 9

[0066] The present invention also provides a pressurization and delivery device for a liquid launch vehicle, comprising the high-pressure electrically controlled valve 1 as described above. By installing a high-pressure electrically controlled valve 1 as described above on the pressurization and delivery device, the high-pressure electrically controlled valve 1 includes a valve assembly 2 and a drive mechanism 3. The first control valve 33 of the drive mechanism 3 is opened or closed by an electrical signal, so that the valve stem 21 of the control valve stem 21 assembly slides axially relative to the valve body 22 within the accommodating cavity 221 of the valve body 22. This enables the connection or isolation of the inlet 223 and outlet 224 on the control valve body 22, thereby achieving remote cutoff or conduction of the high-pressure fluid medium in the pressurization and delivery device of the liquid launch vehicle. Since the opening or closing of the high-pressure electrically controlled valve 1 is relatively smooth, it avoids large impacts during operation, preventing water hammer from occurring on the pressurization and delivery device. It also avoids the generation of excess debris that could affect the normal operation of the pressurization and delivery system due to excessive impacts during use. At the same time, by avoiding the use of pyrotechnics in the high-pressure electrically controlled valve 1, the hardware requirements such as the site and equipment required for its assembly and testing are reduced, and it has the attribute of repetitive work and testing, effectively reducing the manufacturing and operating costs of the high-pressure electrically controlled valve 1, which is conducive to improving the reliability of the liquid launch vehicle.

[0067] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A high-pressure electrically controlled valve for use in a pressurization and delivery device for a liquid-fueled launch vehicle, characterized in that, include: A valve assembly includes a valve stem and a valve body having a receiving cavity. The valve body has a clearance hole at its end for the valve stem to enter the receiving cavity. The valve body has an inlet and an outlet communicating with the receiving cavity and the outside, respectively, and the inlet and outlet are offset from each other. The valve stem has a first sealing protrusion and a second sealing protrusion protruding along its circumferential sidewall to isolate or connect the inlet and the outlet. The first sealing protrusion and the second sealing protrusion are spaced apart, and the diameter of the first sealing protrusion is smaller than the diameter of the second sealing protrusion. The drive mechanism includes a fixed sleeve fixedly connected to the valve body, a piston, a first control valve, and hydraulic oil. The fixed sleeve has a partition that divides the interior of the fixed sleeve into a first inner cavity for inserting the valve stem and a second inner cavity for inserting the piston. The partition has a through hole through which the valve stem passes and is fixedly connected to the piston. The fixed sleeve is equipped with the first control valve, which is used to connect or disconnect the first inner cavity and the second inner cavity. The second sealing protrusion, the partition, and the circumferential inner wall of the fixed sleeve form a first temporary storage area for temporarily storing the hydraulic oil. The piston, the partition, and the circumferential inner wall of the fixed sleeve form a second temporary storage area for temporarily storing the hydraulic oil. When the hydraulic oil is temporarily stored in the first temporary storage area, the inlet and the outlet are in a connected state. When the hydraulic oil is temporarily stored in the second temporary storage area, the inlet and the outlet are in a separated state. The high-pressure electrically controlled valve also includes a position sensor disposed on the valve body. A third sealing protrusion is formed by protruding along the circumferential sidewall of the valve stem. The third sealing protrusion and the second sealing protrusion are spaced apart. The third sealing protrusion is disposed on the opposite side of the second sealing protrusion facing the first sealing protrusion. A first boss, a second boss, and a third boss are sequentially connected on the outer surface of the valve stem between the second sealing protrusion and the third sealing protrusion. The elastic contact of the position sensor is in movable contact with the first boss, the second boss, and the third boss. The working state of the high-pressure solenoid valve is determined by the electrical signal fed back by the elastic contact of the position sensor. When the high-pressure solenoid valve is a normally open solenoid valve, the elastic contact of the position sensor is in a closed state when it abuts against the first boss, in a working state when it abuts against the second boss, and in an open state when it abuts against the third boss; when the high-pressure solenoid valve is a normally closed solenoid valve, the elastic contact of the position sensor is in an open state when it abuts against the first boss, in a working state when it abuts against the second boss, and in a closed state when it abuts against the third boss. The connection between the first boss and the second boss, as well as the connection between the second boss and the third boss, are both provided with inclined surfaces; The valve body has a first vent hole on the end face opposite to one end of the relief hole, which connects the accommodating cavity to the outside. The valve body also has a second vent hole on the side wall at the corresponding position between the second sealing protrusion and the third sealing protrusion of the valve stem, which connects the accommodating cavity to the outside.

2. The high-pressure electrically controlled valve as described in claim 1, characterized in that: The valve stem is provided with a connecting part that is fixedly connected to the piston. The surface of the connecting part, the surface of the first sealing protrusion, the surface of the second sealing protrusion, the surface of the third sealing protrusion, and the surface of the piston are all provided with sealing grooves for installing sealing rings.

3. The high-pressure electrically controlled valve as described in claim 1, characterized in that: The valve stem has a fourth sealing protrusion protruding along its circumferential sidewall. The fourth sealing protrusion is spaced apart from the first sealing protrusion and is located on the opposite side of the first sealing protrusion facing the second sealing protrusion. The diameters of the first sealing protrusion and the fourth sealing protrusion are equal. When the hydraulic oil is temporarily stored in the first temporary storage area, the inlet and the outlet are isolated. When the hydraulic oil is temporarily stored in the second temporary storage area, the inlet and the outlet are connected.

4. The high-pressure electrically controlled valve as described in claim 1, characterized in that: The end of the fixed sleeve is provided with a limiting block for restricting the movement of the piston.

5. The high-pressure electrically controlled valve as described in any one of claims 1 to 4, characterized in that: The high-pressure electrically controlled valve also includes an adjusting nut that is threaded to the end of the fixed sleeve, for driving the piston to move relative to the fixed sleeve in the second inner cavity. The outer surface of the fixed sleeve is provided with a scale for measuring the movement distance of the adjusting nut.

6. The high-pressure electrically controlled valve according to any one of claims 1 to 4, characterized in that: A second control valve is provided on the partition, which is used to connect or disconnect the first inner cavity and the second inner cavity.

7. The high-pressure electrically controlled valve as described in claim 6, characterized in that: The first control valve is a solenoid valve, and the second control valve is a solenoid valve or a check valve.

8. The high-pressure electrically controlled valve according to any one of claims 1 to 4, characterized in that: The outer surface of the valve body is provided with an installation structure.

9. A pressurized delivery device for a liquid-fueled launch vehicle, characterized in that: Includes the high-pressure electrically controlled valve as described in any one of claims 1 to 8.

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