Marine steam differential servo quick-closing valve

Abstract

The invention discloses a marine steam differential servo quick-closing valve, and belongs to the technical field of marine machinery. The marine valve solves the technical problems that an existing marine valve is driven and controlled through an oil source, the occupied space is large, and sealing failure is prone to occurring. The steam chamber comprises a steam outlet chamber, a steam inlet chamber and a discharge chamber which are arranged from top to bottom; the valve seat is fixedly installed on the inner wall between the steam outlet cavity and the steam inlet cavity, the valve disc is in sealing fit with the valve seat, a piston is installed on a valve rod at the lower end of the valve disc, a sealing ring is installed between the piston and the discharging cavity in a matched mode, and a throttling hole is formed in the piston in a penetrating mode in the longitudinal direction. The sleeve is fixed to the upper portion of the steam chamber, and the valve rod at the upper end of the valve disc is sleeved with the lower portion of the sleeve in a sliding mode. A guide rod is in threaded connection with the upper part of the sleeve and can move up and down through rotation; the servo control valve is installed on the lower portion of the discharging cavity and used for adjusting the steam pressure in the discharging cavity, and then the valve disc is controlled to be opened and closed. Unit space is saved, and the structure is reliable. The method is used for steam valve design.

Description

Technical Field

[0001] This invention relates to a marine steam differential servo quick-closing valve, belonging to the field of marine machinery technology. Background Technology

[0002] As the power rating of marine steam turbines increases, the size and weight of valves also increase. Meanwhile, newer ships have even stricter requirements regarding equipment size, weight, unit density, and economic efficiency. Existing marine valves typically use actuators powered by hydraulic or lubricating oil, requiring corresponding control oil pipelines and auxiliary equipment such as control oil stations. This occupies a significant amount of space, and given the limited internal space of the hull, it creates considerable inconvenience for equipment installation, maintenance, and repair. Furthermore, the actuators or auxiliary oil pipeline interfaces are prone to seal failure after prolonged use, posing a risk of oil leakage and potential fire if it comes into contact with high-temperature equipment.

[0003] In summary, existing marine valves, which are driven and controlled by oil, occupy a large space and are prone to sealing failure. Summary of the Invention

[0004] This invention addresses the technical problems of existing marine valves, which occupy a large space due to oil-driven control and are prone to sealing failure. It proposes a marine steam differential servo quick-closing valve, comprising a steam chamber, valve disc, valve seat, piston, sealing ring, servo control valve, sleeve, limit flange, and guide rod. The steam chamber includes an outlet chamber, an inlet chamber, and a discharge chamber arranged from top to bottom; a steam outlet is located on the side of the outlet chamber; and a steam inlet is located on the side of the inlet chamber.

[0005] The valve seat is fixedly installed on the inner wall between the steam outlet chamber and the steam inlet chamber. The valve disc is sealed to the valve seat. A piston is installed on the valve stem at the lower end of the valve disc. A sealing ring is installed between the piston and the discharge chamber. A throttling hole is provided through the piston longitudinally. The sleeve is fixed to the upper part of the steam chamber. The valve stem at the upper end of the valve disc slides into the lower part of the sleeve. A guide rod is threaded to the upper part of the sleeve. The guide rod can move up and down by rotation.

[0006] The area of ​​the steam pressure in the steam inlet chamber acting on the piston in the direction of valve closure is S1;

[0007] The area of ​​the steam pressure in the steam inlet chamber acting on the valve disc in the valve opening direction is S1´;

[0008] The area of ​​the steam pressure in the steam outlet chamber acting on the valve disc in the valve closing direction is S2;

[0009] The area of ​​the vapor pressure in the discharge chamber acting on the piston in the valve opening direction is S3;

[0010] S1, S3, S2 and S1' satisfy the following relationship: S1' < S1 < S3, S2 = S1';

[0011] The servo control valve is installed in the lower part of the discharge chamber. The servo control valve is used to regulate the steam pressure inside the discharge chamber, thereby controlling the valve disc to switch on and off.

[0012] As another improvement of the present invention

[0013] The vapor pressure in the steam inlet chamber is P1, F1 is the pressure that S1 bears, and F1' is the pressure that S1' bears.

[0014] The vapor pressure in the steam outlet chamber is P2, and F2 is the pressure that S2 bears.

[0015] The vapor pressure in the discharge chamber is P3, and F3 is the pressure that S3 withstands.

[0016] ∑F represents the resultant steam force acting on the valve disc, and ∑F satisfies the following relationship: ∑F=F1+F2-F3-F1´.

[0017] When the servo control valve is opened, ∑F > 0, and the valve disc tends to move in the closing direction.

[0018] When the servo control valve is closed, ∑F < 0, and the valve disc tends to move in the opening direction.

[0019] As another improvement of the present invention, the valve seat is installed on the inner wall between the steam outlet chamber and the steam inlet chamber by means of interference fit.

[0020] As another improvement of the present invention, the valve seat is locked by a pressure plate and screws.

[0021] As another improvement of the present invention, the sleeve is fixed to the upper part of the steam chamber by an interference fit.

[0022] As another improvement of the present invention, a limiting flange is installed on the top of the steam chamber to limit the upward movement height of the guide rod.

[0023] As another improvement of the present invention, steam extraction ports are provided on both the upper part of the steam chamber and the sleeve.

[0024] As another improvement of the present invention, the sealing ring installed between the piston and the discharge chamber can be used to buffer the radial vibration of the valve stem on the valve disc.

[0025] As another improvement of the present invention, it also includes a handwheel, which is installed at the top of the guide rod, and the guide rod can be moved up and down by rotating the handwheel.

[0026] As another improvement of the present invention, the handwheel can be rotated manually or electrically.

[0027] The beneficial effects of this invention are:

[0028] This invention employs steam servo control, replacing conventional control mechanisms driven by hydraulic or lubricating oil. It also eliminates the need for traditional control oil pipelines, control oil stations, and other related auxiliary equipment, saving unit space, reducing power requirements, and improving the unit's economic efficiency. Furthermore, it eliminates the risk of oil leakage and fire caused by oil seal failure. The valve utilizes a steam differential principle to achieve both regulation and rapid closing functions. With a servo control valve at the steam discharge point, the steam pressure in the discharge chamber can be adjusted in real time, and its interaction with the steam in the inlet and outlet chambers achieves force balance matching on the valve disc, enabling regulation and control of the valve's full stroke position. When the servo control valve rapidly discharges steam, the valve achieves rapid closing. Attached Figure Description

[0029] Figure 1 This is a schematic diagram of the overall structure of a marine steam differential servo quick-closing valve according to the present invention. Detailed Implementation

[0030] The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0031] Specific implementation method one: Combining Figure 1 This embodiment describes a marine steam differential servo quick-closing valve, characterized in that it includes a steam chamber 1, a valve disc 2, a valve seat 3, a piston 4, a sealing ring 5, a servo control valve 6, a sleeve 8, a limiting flange 9, and a guide rod 10. The steam chamber 1 includes an outlet chamber, an inlet chamber, and a discharge chamber arranged from top to bottom; a steam outlet is provided on the side of the outlet chamber; and a steam inlet is provided on the side of the inlet chamber.

[0032] Valve seat 3 is fixedly installed on the inner wall between the steam outlet chamber and the steam inlet chamber. Valve disc 2 is sealed to valve seat 3. A piston 4 is installed on the valve stem at the lower end of valve disc 2. A sealing ring 5 is installed between piston 4 and discharge chamber. A throttling hole is provided through piston 4 in the longitudinal direction. Sleeve 8 is fixed to the upper part of steam chamber 1. Valve stem at the upper end of valve disc 2 is slidably inserted into the lower part of sleeve 8. A guide rod 10 is threadedly connected to the upper part of sleeve 8. The guide rod 10 can move up and down by rotation.

[0033] The area of ​​the steam pressure in the steam inlet chamber acting on piston 4 in the direction of valve closure is S1;

[0034] The area of ​​the steam pressure in the steam inlet chamber acting on valve disc 2 in the valve opening direction is S1´;

[0035] The area of ​​the steam pressure in the steam outlet chamber acting on valve disc 2 in the valve closing direction is S2;

[0036] The area of ​​the vapor pressure in the discharge chamber acting on piston 4 in the valve opening direction is S3;

[0037] S1, S3, S2 and S1' satisfy the following relationship: S1' < S1 < S3, S2 = S1';

[0038] Servo control valve 6 is installed at the lower part of the discharge chamber. Servo control valve 6 is used to regulate the steam pressure inside the discharge chamber, thereby realizing the opening and closing action of control valve disc 2. In this embodiment, the discharge chamber pressure is regulated by introducing steam through a throttling orifice and discharging steam through the servo control valve. Alternatively, other types of switching valves or steam inlet and outlet methods can be used to regulate the chamber pressure.

[0039] The valve achieves both regulation and rapid closing functions by adopting the steam differential principle. After the servo control valve is configured at the steam discharge point, the steam pressure in the discharge chamber can be adjusted in real time through the servo control valve, and the steam in the inlet and outlet chambers can work together to achieve force balance matching on the valve disc, realizing the regulation and control of the valve position throughout its entire stroke. When the servo control valve discharges steam rapidly, the valve achieves the rapid closing function.

[0040] Specific Implementation Method Two: Combining Figure 1 This embodiment differs from specific embodiment one in that the vapor pressure in the steam inlet chamber is P1, F1 is the pressure that S1 bears, and F1' is the pressure that S1' bears.

[0041] The vapor pressure in the steam outlet chamber is P2, and F2 is the pressure that S2 bears.

[0042] The vapor pressure in the discharge chamber is P3, and F3 is the pressure that S3 withstands.

[0043] ∑F represents the resultant steam force acting on valve disc 2, and ∑F satisfies the following relationship: ∑F=F1+F2-F3-F1´.

[0044] When the servo control valve 6 is opened, ∑F > 0, and the valve disc 2 tends to move in the closing direction.

[0045] When the servo control valve 6 is closed, ∑F < 0, and valve disc 2 tends to move in the opening direction.

[0046] Steam in the inlet chamber P1 can flow into the outlet chamber P3 through the throttle orifice, and cooperate with the servo control valve 6 to change the steam pressure in the outlet chamber P3, thereby changing the vertical upward steam force F3 of the steam in the outlet chamber P3 on the piston 4.

[0047] The marine steam differential servo quick-closing valve of the present invention has two control modes: manual and automatic.

[0048] When the valve is manually opened or closed, the servo control valve 6 is completely closed. At this time, the steam pressure in the three chambers satisfies P1 = P3 > P2. Since S1 < S3 and S2 = S1' in the design structure, F1 < F3 and F2 < F1', so ∑F < 0. That is, the entire valve disc assembly is subjected to steam force in the opening direction. When the handwheel 11 is rotated counterclockwise to make the guide rod 10 move upward, the valve disc will move upward synchronously, and the valve will gradually open. L is the maximum opening degree that the valve can reach. Conversely, the valve is closed by rotating the handwheel in the opposite direction.

[0049] When the automatic control valve opens and closes, the servo control valve 6 can be fully opened first. At this time, the steam pressure in the three chambers satisfies P1>P3≈0 and P1>P2. Since S1>S1´ in the design structure, F3≈0 and F1>F1´, therefore ∑F>0, meaning the entire valve disc assembly is subjected to steam force in the closing direction. During the process of rotating the handwheel 11 counterclockwise to move the guide rod 10 upward to its maximum position, the valve disc remains stationary under the downward steam resultant force. During the gradual closing of the servo control valve, the steam resultant force on the valve disc assembly gradually changes from the closing direction to the opening direction, thus realizing the gradual opening of the valve; conversely, the valve gradually closes. The servo control valve 6 can control the steam pressure in the discharge chamber, thereby achieving a pressure matching balance with the inlet and outlet chambers to achieve full-stroke position adjustment control of the valve. When the servo control valve 6 quickly discharges steam, the valve achieves a quick-closing function. Other components and connection methods are the same as in specific implementation method one.

[0050] Specific implementation method three: Combining Figure 1 This embodiment differs from specific embodiment one in that the valve seat 3 is installed on the inner wall between the steam outlet chamber and the steam inlet chamber via an interference fit. This design ensures structural reliability and convenient installation. Other components and connection methods are the same as in specific embodiment one or two.

[0051] Specific implementation method four: Combination Figure 1 This embodiment differs from specific embodiment one in that the valve seat 3 is locked in place by the pressure plate 7 and screws. This design ensures structural reliability. Other components and connection methods are the same as in any one of specific embodiments one through three.

[0052] Specific Implementation Method Five: Combining Figure 1 This embodiment differs from specific embodiment one in that the sleeve 8 is fixed to the upper part of the steam chamber 1 by an interference fit. This design ensures structural reliability and convenient installation. Other components and connection methods are the same as any one of specific embodiments one through four.

[0053] Specific Implementation Method Six: Combination Figure 1 This embodiment differs from specific embodiment one in that a limiting flange 9 is installed at the top of the steam chamber 1 to limit the upward movement height of the guide rod 10. The downward movement of the guide rod 10 is limited when the lower end face of the guide rod contacts the valve stem at the upper end of the valve disc 2 until the valve is closed. Other components and connection methods are the same as any one of specific embodiments one to five.

[0054] Specific implementation method seven: Combination Figure 1 This embodiment differs from specific embodiment one in that both the upper part of the steam chamber 1 and the sleeve 8 have steam extraction ports. Other components and connection methods are the same as any one of specific embodiments one through six.

[0055] Specific implementation method eight: Combination Figure 1 This embodiment differs from specific embodiment one in that the sealing ring 5, which is fitted between the piston 4 and the discharge chamber, can be used to buffer the radial vibration of the valve stem on the valve disc 2. The sealing ring can act as an elastic damping element to buffer the radial vibration of the valve stem. Other components and connection methods are the same as any one of specific embodiments one to seven.

[0056] Specific Implementation Method Nine: Combining Figure 1 This embodiment differs from specific embodiment one in that it also includes a handwheel 11. The handwheel 11 is mounted on the top of the guide rod 10, and rotating the handwheel 11 moves the guide rod 10 up and down. The handwheel can also be replaced by a lever lifting method. Other components and connection methods are the same as any one of specific embodiments one to eight.

[0057] Specific Implementation Method Ten: Combining Figure 1 This embodiment differs from specific embodiment one in that the handwheel 11 can be rotated manually or electrically. Other components and connections are the same as in any one of specific embodiments one through nine.

[0058] Combination Figure 1 Explanation of the working principle of this invention:

[0059] When the valve is manually opened or closed, the servo control valve 6 is completely closed. At this time, the steam pressure in the three chambers satisfies P1 = P3 > P2. Since S1 < S3 and S2 = S1' in the design structure, F1 < F3 and F2 < F1', so ∑F < 0. That is, the entire valve disc assembly is subjected to steam force in the opening direction. When the handwheel 11 is rotated counterclockwise to make the guide rod 10 move upward, the valve disc will move upward synchronously, and the valve will gradually open. L is the maximum opening degree that the valve can reach. Conversely, the valve is closed by rotating the handwheel in the opposite direction.

[0060] When the automatic control valve opens and closes, the servo control valve 6 can be fully opened first. At this time, the steam pressure in the three chambers satisfies P1>P3≈0 and P1>P2. Since S1>S1´ in the design structure, F3≈0 and F1>F1´, therefore ∑F>0, meaning the entire valve disc assembly is subjected to steam force in the closing direction. During the process of rotating the handwheel 11 counterclockwise to move the guide rod 10 upward to its maximum position, the valve disc remains stationary under the downward steam force. During the gradual closing of the servo control valve, the steam force on the valve disc assembly gradually changes from the closing direction to the opening direction, thus gradually opening the valve; conversely, the valve gradually closes. The servo control valve 6 can control the steam pressure in the discharge chamber, thereby achieving a pressure matching balance with the inlet and outlet chambers to regulate the valve's full stroke position. When the servo control valve 6 rapidly discharges steam, the valve achieves a rapid closing function.

[0061] The above embodiments are only used to illustrate the technical solutions of the present invention, and are not intended to limit it. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A marine steam differential servo quick-closing valve, characterized in that... It includes a steam chamber (1), a valve disc (2), a valve seat (3), a piston (4), a sealing ring (5), a servo control valve (6), a sleeve (8), a limit flange (9), and a guide rod (10). The steam chamber (1) includes an outlet chamber, an inlet chamber, and an exhaust chamber arranged from top to bottom. A steam outlet is provided on the side of the outlet chamber. A steam inlet is provided on the side of the inlet chamber. The valve seat (3) is fixedly installed on the inner wall between the steam outlet chamber and the steam inlet chamber. The valve disc (2) is sealed to the valve seat (3). The valve stem at the lower end of the valve disc (2) is fitted with a piston (4). A sealing ring (5) is fitted between the piston (4) and the discharge chamber. The piston (4) has a throttling hole through it in the longitudinal direction. The sleeve (8) is fixed to the upper part of the steam chamber (1). The valve stem at the upper end of the valve disc (2) is slidably fitted into the lower part of the sleeve (8). The upper part of the sleeve (8) is threaded with a guide rod (10). The guide rod (10) can move up and down by rotation. The area of ​​the steam pressure in the steam inlet chamber acting on the piston (4) in the valve closing direction is S1; The area of ​​the steam pressure in the steam inlet chamber acting on the valve disc (2) in the valve opening direction is S1´; The area of ​​the steam pressure in the steam outlet chamber acting on the valve disc (2) in the valve closing direction is S2; The area of ​​the vapor pressure in the discharge chamber acting on the piston (4) in the valve opening direction is S3; S1, S3, S2 and S1' satisfy the following relationship: S1' < S1 < S3, S2 = S1'; The servo control valve (6) is installed in the lower part of the discharge chamber. The servo control valve (6) is used to regulate the steam pressure inside the discharge chamber, thereby realizing the opening and closing action of the control valve disc (2).

2. The marine steam differential servo quick-closing valve according to claim 1, characterized in that, The vapor pressure in the steam inlet chamber is P1, F1 is the pressure that S1 bears, and F1' is the pressure that S1' bears. The vapor pressure in the steam outlet chamber is P2, and F2 is the pressure that S2 bears. The vapor pressure in the discharge chamber is P3, and F3 is the pressure that S3 withstands. ∑F is the resultant steam force on valve disc (2), and ∑F satisfies the following relationship: ∑F=F1+F2-F3-F1´, When the servo control valve (6) is opened, ∑F > 0, and the valve disc (2) tends to move in the closing direction; When the servo control valve (6) is closed, ∑F < 0, and the valve disc (2) tends to move in the opening direction.

3. A marine steam differential servo quick-closing valve according to claim 1, characterized in that, The valve seat (3) is installed on the inner wall between the steam outlet chamber and the steam inlet chamber by means of interference fit.

4. A marine steam differential servo quick-closing valve according to claim 1, characterized in that, The valve seat (3) is locked in place by the pressure plate (7) and screws.

5. A marine steam differential servo quick-closing valve according to claim 1, characterized in that, The sleeve (8) is fixed to the upper part of the steam chamber (1) by interference fit.

6. A marine steam differential servo quick-closing valve according to claim 1, characterized in that, A limiting flange (9) is installed on the top of the steam chamber (1) to limit the upward movement height of the guide rod (10).

7. A marine steam differential servo quick-closing valve according to claim 1, characterized in that, Steam extraction ports are provided on the upper part of the steam chamber (1) and on the sleeve (8).

8. A marine steam differential servo quick-closing valve according to claim 1, characterized in that, The sealing ring (5) installed between the piston (4) and the discharge chamber can be used to buffer the radial vibration of the valve stem on the valve disc (2).

9. A marine steam differential servo quick-closing valve according to claim 1, characterized in that... It also includes a handwheel (11), which is installed at the top of the guide rod (10). The guide rod (10) moves up and down by rotating the handwheel (11).

10. A marine steam differential servo quick-closing valve according to claim 9, characterized in that, The handwheel (11) can be turned manually or electrically.

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