Passive anti-heeling device special for emergency floating and working process

Abstract

The passive anti-heeling device special for emergency floating comprises a boat body assembly, wing assemblies are symmetrically arranged at the two ends of the boat body assembly, each wing assembly is supported through a set of spaced rudder shaft bases, the rudder shaft bases are arranged in the boat body assembly, and an oil cylinder assembly is installed between the two rudder shaft bases; a limiting assembly is installed on the oil cylinder assembly, and an upper sliding block and a lower sliding block which are spaced up and down are installed in the oil cylinder assembly. Each wing assembly structurally comprises a wing plate, a rotating shaft and a rotating shaft key, the wing plate is arranged outside the boat body assembly, the gravity center of the wing plate is located on the axis of the rotating shaft, the axis of the rotating shaft is perpendicular to the middle longitudinal section of the boat body assembly, the rotating shaft penetrates through the whole oil cylinder assembly, and the bottom face of the rotating shaft key is fixedly connected to the rotating shaft of the middle section in the oil cylinder assembly. The upper sliding block and the lower sliding block are the same in structure, the upper sliding block structurally comprises a first balance weight plate arranged in the middle of the oil cylinder assembly, first ball sliding blocks are arranged on the two sides of the first balance weight plate respectively, and use is flexible and convenient.

Description

Technical Field

[0001] The present invention relates to the technical field of emergency surfacing equipment for submersibles, and in particular to a passive anti-heeling device and working process dedicated to emergency surfacing. Background Art

[0002] In deep-sea operations at ultra-large diving depths, submersibles adopt a structural form of multiple small pressure-resistant cabins, which can reduce the construction difficulty, improve the pressure resistance, and reduce the equipment weight. In the ultra-high pressure environment of the deep sea, once a pipeline is damaged or a pressure-resistant cabin is breached, the seawater inflow rate is extremely high, and the inflow volume is large, resulting in a rapid diving of the submersible. The propulsion power of work-type deep submersibles is small, and the anti-sinking ability is weak. The jettison device is the most effective solution. However, large jettison devices can usually only jettison within a specific heeling angle of the hull. For submersibles with multiple lateral pressure-resistant cabins arranged, when seawater enters one side of the pressure-resistant cabins, a heeling angle much larger than that in the conventional situation will be generated, resulting in the inability to jettison and threatening the safety of the hull.

[0003] In order to achieve smooth jettison, it is necessary to restore the hull to within the allowable heeling angle, that is, anti-heeling measures need to be taken. In the case of serious failures such as cabin flooding and equipment damage, systems such as power, hydraulic, or control are difficult to ensure still working, and the anti-risk ability is weak. Only a self-contained device with strong anti-interference ability can be used as the final insurance.

[0004] During jettison and surfacing, the inflow volume reduces the effect of jettison, resulting in a slow surfacing speed and weak emergency recovery ability. The horizontal fins of the submersible have a large resistance during surfacing, which is also not conducive to the stability of the hull attitude and has an adverse impact on safe surfacing.

[0005] For the above problems, there is no systematic and lightweight, cost-effective solution, and a new solution is urgently needed. Summary of the Invention

[0006] The applicant of the present invention aims at the above-mentioned disadvantages in the existing production technology and provides a passive anti-heeling device and working process dedicated to emergency surfacing with a reasonable structure, so that it works stably, is flexible and convenient to use, and greatly improves the anti-sinking ability.

[0007] The technical solution adopted by the present invention is as follows:

[0008] A passive anti - heeling device dedicated to emergency surfacing, comprising a hull assembly. Wing assemblies are symmetrically arranged at both ends of the hull assembly. A single wing assembly is supported by a set of spaced rudder shaft bases which are arranged inside the hull assembly. An oil cylinder assembly is installed between two rudder shaft bases. A limit assembly is installed on the oil cylinder assembly. An upper slider and a lower slider are installed at intervals inside the oil cylinder assembly. The structure of a single wing assembly is as follows: it includes a wing plate, a rotating shaft and a rotating shaft key. The wing plate is arranged outside the hull assembly. The center of gravity of the wing plate is located on the axis of the rotating shaft. The axis of the rotating shaft is perpendicular to the longitudinal mid - section of the hull assembly. The rotating shaft passes through the entire oil cylinder assembly. The bottom surface of the rotating shaft key is fixedly connected to the rotating shaft in the middle section inside the oil cylinder assembly. The upper slider and the lower slider have the same structure. The structure of the upper slider is as follows: it includes a first counterweight plate arranged in the middle of the oil cylinder assembly, and two first ball sliders are respectively arranged on both sides of the first counterweight plate.

[0009] As a further improvement of the above - mentioned technical solution:

[0010] The structure of the hull assembly is as follows: it includes a light outer shell. A plurality of pressure - resistant cabins are arranged inside the light outer shell. A throw - off load is arranged at the bottom of the hull.

[0011] The rotating shaft adopts a rigid cylindrical shaft.

[0012] The rotating shaft key adopts a cuboid rigid key with a rounded head, and the surface of the rotating shaft key is provided with a rubber layer.

[0013] The thickness of the rotating shaft key is the same as the gap between the upper slider and the lower slider 4.

[0014] The structure of the oil cylinder assembly is as follows: it includes an oil cylinder shell. Both sides of the bottom of the oil cylinder shell are provided with mounting ear plates. The mounting ear plates are fixed on the hull through fasteners. The inside of the oil cylinder shell is filled with lubricating oil. Two threaded through - holes for installing the limit assembly are provided on the right - hand side wall of the oil cylinder shell.

[0015] The oil cylinder shell adopts a cuboid thin - shell structure.

[0016] The structure of the limit assembly is as follows: it includes a limit nut installed in the threaded through - hole. The limit nut extends deep into the oil cylinder and respectively presses on the end faces of the upper slider and the lower slider. It also includes a limit rope. One end of the limit rope is connected to the front wall surface inside the oil cylinder shell, and the other end is connected to the front end face of the upper slider.

[0017] The limit rope adopts a lightweight, soft and rigid rope.

[0018] The working process of a passive anti - heeling device dedicated to emergency surfacing includes the following processes:

[0019] When used as a stabilizing fin:

[0020] When the response roll angle is the same as the maximum allowable roll angle of the ballast device, the roll angle of the submersible will not exceed the response roll angle of the passive anti-roll device. The upper slider and the lower slider cannot break through the limit of the limit nut, continuously lock the rotating shaft, restrict rotation, maintain the wing plate in a horizontal state, and realize the function of the stabilizer fin;

[0021] When used for emergency surfacing:

[0022] The passive anti-roll devices are symmetrically installed on the left and right, and have the same effect in left and right rolling;

[0023] When the submersible rapidly sinks with a large roll angle due to a broken cabin and water ingress underwater, if the roll angle exceeds the maximum allowable roll angle of the ballast mechanism, the ballast mechanism cannot perform ballasting. Since the response roll angle is the same as the maximum allowable roll angle of the ballast device, this passive anti-roll device is triggered to work at this time;

[0024] At this time, the gravity drives the slider to slide to overcome the limit of the limit nut, partially releasing the rotation restriction of the wing plate; the wing plate on the lifting side turns into a vertical state and self-locks under the action of the underwater flow force; the wing plate on the sinking side maintains a horizontal state, and the wing plates on both sides generate an anti-roll hydrodynamic moment during the depth-drop process, reducing the roll angle and facilitating ballasting;

[0025] After ballasting, during the ascent of the submersible, the wing plate on the sinking side turns into a vertical state and locks under the action of the flow force, reducing the ascent resistance and enhancing the attitude stability.

[0026] The beneficial effects of the present invention are as follows:

[0027] The structure of the present invention is compact, reasonable, and easy to operate. Through the mutual cooperation of components such as the wing assembly, rudder shaft base, upper slider, lower slider, limit assembly, oil cylinder assembly, and hull assembly, the switching of the attitude of the wing plate can be conveniently completed. It is used as a horizontal stabilizer fin under normal conditions. When the submersible has a broken cabin and sinks with a large roll angle and cannot perform ballasting, the rotation restriction of the wing plate on the lifting side will be automatically released and turn into a vertical state, while the wing plate on the other side still maintains a horizontal state. The left and right wings generate an anti-roll moment during the depth-drop, reducing the roll angle and facilitating ballasting. When it turns to ascent after ballasting, the wing plate on the sinking side automatically turns into a vertical state and locks under the action of the hydrodynamic force, eliminating the unbalanced force, reducing the ascent resistance, and improving the ascent speed and stability. The present invention does not require a steering gear and energy, has an independent structure, strong anti-risk ability, does not affect the function of the stabilizer fin, enhances the safety reserve, and improves the anti-sinking ability.

[0028] At the same time, the present invention also has the following advantages:

[0029] 1) When the submersible sinks with a large roll angle due to a broken cabin, the single-sided horizontal wing plate will automatically turn into a vertical state, forming a righting moment, weakening the roll angle, and facilitating the ballast mechanism to perform ballasting smoothly.

[0030] 2) When the submersible turns to float after jettisoning the load, the other wing plate also turns to the vertical state, reducing the floating resistance, increasing the floating speed, and enhancing the stability of the attitude.

[0031] 3) Expand the function of the existing stabilizing fins of the hull with minor modifications and strong practicability. During normal navigation, they still act as stabilizing fins and will not have an additional impact on the hull.

[0032] 4) It does not require a steering gear, energy source, and control system. It has an independent structure, does not require pressure resistance, has a simple structure, light weight, and high reliability, and can be used as a conventional safety reserve device.

[0033] 5) Through mechanical transmission, the large rotational force of the rotating shaft is changed into a sliding force that is easy to control, and it can be conveniently limited and locked by a limit nut to avoid damage to the equipment caused by large dynamic loads.

[0034] 6) The transverse tilt response angle can be adjusted by adjusting the limit nut, which is convenient to operate and has a wide adaptability. Brief Description of the Drawings

[0035] Figure 1 It is a schematic installation diagram of the passive anti - transverse tilt device dedicated to emergency floating in the submersible according to the present invention.

[0036] Figure 2 It is a structural diagram of the left wing rotation when the passive anti - transverse tilt device dedicated to emergency floating in the submersible according to the present invention has a serious large transverse tilt.

[0037] Figure 3 It is a structural diagram of the right wing rotation when the submersible turns to float after jettisoning the load with the passive anti - transverse tilt device dedicated to emergency floating in the submersible according to the present invention.

[0038] Figure 4 It is a schematic structural diagram of the left - wing device of the present invention.

[0039] Figure 5 It is a schematic internal structural diagram of the left - wing device of the present invention.

[0040] Figure 6 It is a state diagram of the left - wing rotation when the submersible has a large transverse tilt and drops depth according to the present invention.

[0041] Figure 7 It is a state diagram of the right - wing rotation when the submersible has a large transverse tilt and drops depth according to the present invention.

[0042] Figure 8 It is a state diagram of the right - wing rotation when the submersible turns to float after jettisoning the load according to the present invention.

[0043] Wherein:

[0044] 1. Wing assembly; 2. Rudder shaft base; 3. Upper slider; 4. Lower slider; 5. Limit assembly; 6. Oil cylinder assembly; 7. Hull assembly;

[0045] 11. Wing plate; 12. Rotating shaft; 13. Rotating shaft key;

[0046] 31. First counterweight plate; 32. First ball slider;

[0047] 41. Second counterweight plate; 42. Second ball slider;

[0048] 51. Limit nut; 52. Limit rope;

[0049] 61. Oil cylinder shell; 62. Upper slide rail; 63. Lower slide rail;

[0050] 71. Light outer shell; 72. Pressure-resistant cabin; 73. Jettisonable load. Detailed implementation manners

[0051] The following combines with the attached drawings to illustrate the detailed implementation manners of the present invention.

[0052] As Figures 1-7 shown, the passive anti-heeling device dedicated to emergency surfacing in this embodiment includes a hull assembly 7. Wing assemblies 1 are symmetrically arranged at both ends of the hull assembly 7. A single wing assembly 1 is supported by a group of spaced rudder shaft bases 2. The rudder shaft bases 2 are arranged inside the hull assembly 7. An oil cylinder assembly 6 is installed between the two rudder shaft bases 2. A limit assembly 5 is installed on the oil cylinder assembly 6. An upper slider 3 and a lower slider 4 are installed at intervals inside the oil cylinder assembly 6. The structure of a single wing assembly 1 is: including a wing plate 11, a rotating shaft 12 and a rotating shaft key 13. The wing plate 11 is arranged outside the hull assembly 7. The center of gravity of the wing plate 11 is located on the axis of the rotating shaft 12. The axis of the rotating shaft 12 is perpendicular to the mid-longitudinal section of the hull assembly 7. The rotating shaft 12 penetrates through the entire oil cylinder assembly 6. The bottom surface of the rotating shaft key 13 is fixedly connected to the rotating shaft 12 in the middle section inside the oil cylinder assembly 6. The upper slider 3 and the lower slider 4 have the same structure. The structure of the upper slider 3 is: including a first counterweight plate 31 arranged in the middle of the oil cylinder assembly 6. First ball sliders 32 are respectively arranged on both sides of the first counterweight plate 31.

[0053] The structure of the hull assembly 7 is: including a light outer shell 71. A plurality of pressure-resistant cabins 72 are arranged inside the light outer shell 71. A jettisonable load 73 is arranged at the bottom of the hull.

[0054] The rotating shaft 12 adopts a rigid cylindrical shaft.

[0055] The rotating shaft key 13 adopts a cuboid rigid key with a rounded head. The surface of the rotating shaft key 13 is provided with a rubber layer.

[0056] The thickness of the rotating shaft key 13 is the same as the gap between the upper slider 3 and the lower slider 4.

[0057] The structure of the oil cylinder assembly 6 is as follows: It includes an oil cylinder housing 61. Both sides of the bottom of the oil cylinder housing 61 are provided with mounting ear plates, and the mounting ear plates are fixed on the hull by fasteners. The inside of the oil cylinder housing 61 is filled with lubricating oil, and there are two threaded through holes for mounting the limiting assembly 5 on the right side wall of the oil cylinder housing 61.

[0058] The oil cylinder housing 61 adopts a cuboid thin shell structure.

[0059] The structure of the limiting assembly 5 is as follows: It includes a limiting nut 51 installed in the threaded through hole. The limiting nut 51 extends deep into the oil cylinder and presses against the end faces of the upper sliding block 3 and the lower sliding block 4 respectively; it also includes a limiting rope 52. One end of the limiting rope 52 is connected to the front wall surface inside the oil cylinder housing 61, and the other end is connected to the front end face of the upper sliding block 3.

[0060] The limiting rope 52 adopts a lightweight, soft and rigid rope.

[0061] The specific structure and function of the passive anti - rolling device dedicated to emergency surfacing of the present invention are as follows:

[0062] Two sets of the devices are provided and are symmetrically installed on both sides of the submersible hull.

[0063] This embodiment only describes the composition of the left - wing device. In this embodiment, the length inside the oil cylinder refers to the length along the axis direction of the rotating shaft 12.

[0064] It mainly includes a wing assembly 1, a rudder shaft base 2, an upper sliding block 3, a lower sliding block 4, a limiting assembly 5, an oil cylinder assembly 6 and a hull assembly 7.

[0065] Among them, the wing assembly 1 includes a wing plate 11, a rotating shaft 12 and a rotating shaft key 13.

[0066] The wing plate 11 - - The center of gravity is located on the axis of the rotating shaft 12, and the area behind the rotating shaft 12 is larger than the area in front.

[0067] The rotating shaft 12 - - It is a rigid cylindrical shaft, and the axis of the rotating shaft 12 is perpendicular to the mid - longitudinal section of the hull.

[0068] The rotating shaft key 13 - - It is a cuboid rigid key with a rounded head and a rubber layer on the surface.

[0069] The bottom surface of the rotating shaft key 13 is fixedly connected to the rotating shaft 12 in the middle section inside the oil cylinder. The thickness of the rotating shaft key 13 is the same as the gap between the upper sliding block 3 and the lower sliding block 4, and the minor - axis diameter during rotation is slightly larger than the height inside the oil cylinder. The distance between the front and rear end faces of the rotating shaft key 13 and the front and rear inner wall surfaces of the oil cylinder is one - third of the length inside the oil cylinder.

[0070] Among them, there are two rudder shaft bases 2 in total, which are used to support and fix the rudder shaft and allow the rudder shaft to rotate around the rudder shaft axis with low resistance.

[0071] Among them, the upper slider 3 is composed of a No. 1 counterweight plate 31 in the middle and two No. 1 ball sliders 32 on the left and right.

[0072] The No. 1 counterweight plate 31 is a cuboid rigid plate with a certain weight, and its length in the axis direction of the rotating shaft 12 is one-third of the length inside the oil cylinder.

[0073] There are two No. 1 ball sliders 32 in total, which are symmetrically fixed on the left and right sides of the No. 1 counterweight plate 31 and sleeved on two upper slide rails 62 respectively. The No. 1 ball slider 32 is internally provided with balls, which can achieve low-resistance sliding with the slide rail. The outer end face of the No. 1 ball slider 32 is a plane.

[0074] Among them, the lower slider 4 includes a No. 2 counterweight plate 41 and a No. 2 ball slider 42. The structure of the lower slider 4 is the same as that of the upper slider 3, and it is only installed on the lower slide rail 63.

[0075] Among them, the limiting component 5 includes limiting nuts 51, which are threaded nuts with a plane bottom. There are two in total, and they are respectively installed on two threaded through holes on the oil cylinder housing 61. The limiting nuts 51 extend into the oil cylinder and respectively press on the end faces of the upper slider 3 and the lower slider 4.

[0076] Among them, the oil cylinder assembly 6 includes an oil cylinder housing 61, which is a cuboid thin shell structure with mounting ear plates on both sides of the bottom and is fixedly connected to the hull. The inside of the oil cylinder housing 61 is filled with lubricating oil, and there are two threaded through holes on the right side wall surface.

[0077] The upper slide rail 62 is a cylindrical shaft, and there are two in total, parallel to the rotating shaft 12. The upper slide rail 62 is located inside the oil cylinder housing 61, and both ends are fixedly connected to the front and rear housings of the oil cylinder.

[0078] The lower slide rail 63 has the same structural composition as the upper slide rail 62. The upper slide rail 62 and the lower slide rail 63 are symmetric about the horizontal symmetry plane of the oil cylinder housing 61.

[0079] The limiting rope 52 is a light, soft and rigid rope with a length of one-third of the length inside the oil cylinder. One end of the limiting rope 52 is connected to the front wall surface inside the oil cylinder, and the other end is connected to the front end face of the No. 1 counterweight plate 31 in the upper slider 3. The two connection points of the limiting rope 52 are at the same height and are directly above the rotating shaft 12.

[0080] The rotation of the wing in response to the roll angle is the minimum roll angle for the slider to overcome the limit of the limiting nut 51 and move along the slide rail, and it is set by adjusting the weights of the upper and lower counterweight plates and the squeezing friction force of the limiting nut 51 on the slider.

[0081] The rotation of the wing responds to the roll angle and is the same as the maximum allowable roll angle of the ballast device.

[0082] During the actual working process:

[0083] This device has two uses and automatically switches according to the situation, specifically as follows:

[0084] (1) Use as a stabilizer fin:

[0085] Since the allowable roll angle of the ballast device is usually large, such as 40°, during daily navigation, the probability of a large roll angle due to a damaged compartment is low, and the roll angle of the submersible generally does not exceed the maximum allowable roll angle of the ballast device. Since the response roll angle of this device is the same as the maximum allowable roll angle of the ballast device, the roll angle of the submersible will not exceed the response roll angle of this device. Therefore, the upper slider 3 and the lower slider 4 are restricted by the limit nut 51 and will not slide, thereby locking the rotating shaft 12 and restricting its rotation, maintaining the wing plate 11 in a horizontal state and realizing the function of the stabilizer fin.

[0086] (2) Application in emergency surfacing:

[0087] This device is installed symmetrically left and right, and has the same effect in left and right roll. Only the right roll is taken as an example in this embodiment for illustration.

[0088] When the pressure-resistant compartment on one side of the submersible in deep sea is flooded, the metacentric height of the submersible decreases, and it sinks rapidly with a large roll angle.

[0089] When the right roll angle of the submersible quickly exceeds the maximum allowable roll angle of the ballast mechanism, the ballast mechanism cannot perform ballasting. Since the response roll angle of the wing is the same as the maximum allowable roll angle of the ballast mechanism, the roll angle at this time is greater than the response roll angle of the rudder, triggering the rotation of the wing plate 11.

[0090] The specific process is as follows:

[0091] After the submersible tilts to the right, the upper slider 3 and the lower slider 4 in the left wing overcome the restriction force of the limit nut 51 under their own gravity and slide to the lower right of the oil cylinder, releasing the rotation restriction on the upper shaft key 13 of the left rotating shaft 12.

[0092] Since the underwater center of gravity of the wing plate 11 is located on the axis of the rotating shaft 12, the rotation of the wing is only dominated by hydrodynamic forces. When diving with a depth drop, the water flow impacts the wing plate 11 from bottom to top. The area behind the rotating shaft 12 is larger than the front, and the unbalanced ocean current moment causes the trailing edge of the wing plate 11 to rotate upward.

[0093] Due to the relatively high speed of depth drop, the hydrodynamic torque acting on the wing plate 11 is relatively large. Coupled with the fact that the wing plate 11 has a certain weight and has a large kinetic energy before the rotation stops. When the rudder rotates to the vertical state, since the oval diameter of the key of the rotating shaft 13 is slightly larger than the inner height of the oil cylinder, the key of the rotating shaft 13 will be pressed against the inner wall surface of the oil cylinder, generating a frictional locking force to achieve the limit of the rudder angle. After the rotation stops, the left wing always maintains the vertical state, the vertical windward area decreases, and the rudder force disappears.

[0094] For the right wing, when the upper slider 3 moves to the right, it is restricted by the limiting rope 52 and cannot move. The lower slider 4 overcomes the limit of the limiting nut 51 under its own gravity and slides to the right side of the key of the rotating shaft 13, releasing the restriction on the downward rotation of the key of the rotating shaft 13. However, before the ballast is jettisoned, the submersible is in a high-speed diving state, and the hydrodynamic force causes the trailing edge of the unbalanced rudder to rotate upward, driving the key of the rotating shaft 13 to rotate upward and get stuck on the upper slider 3, unable to rotate. Therefore, it dives while maintaining the straight state of the right wing.

[0095] The left wing turns to the vertical state, and the right wing remains in the horizontal state. During the depth drop, the left and right wings will generate an anti-rolling moment, reducing the roll angle of the hull.

[0096] After the roll of the submersible decreases, the submersible successfully jettisons the ballast and changes from diving to surfacing.

[0097] During surfacing, the water flow flushes the right wing from top to bottom. Since the area behind the wing plate 11 is larger than the front, the wing plate 11 generates a hydrodynamic torque for the trailing edge to turn downward. After the lower slider 4 is removed, it no longer restricts the downward rotation of the key of the rotating shaft 13. The wing plate 11 drives the key of the rotating shaft 13 to rotate downward through the rotating shaft 12. Since the oval diameter of the key of the rotating shaft 13 is slightly larger than the inner height of the oil cylinder, when the wing plate 11 rotates to near the vertical state, the key of the rotating shaft 13 is pressed against the inner bottom surface of the oil cylinder, generating a frictional locking force to achieve the limit of the angle of the wing plate 11.

[0098] During the entire surfacing process, the left and right wings of the submersible are in the locked vertical state, reducing the surfacing resistance, increasing the surfacing speed, enhancing the attitude stability, and improving the emergency anti-sinking ability.

[0099] The above description is an explanation of the present invention, not a limitation of the invention. The scope defined by the present invention is referred to the claims. Within the protection scope of the present invention, any form of modification can be made.

Claims

1. A passive anti-heeling device specially used for emergency buoyancy, characterized by: The invention comprises a hull assembly (7), wherein wing assemblies (1) are symmetrically arranged at both ends of the hull assembly (7), a single wing assembly (1) is supported by a group of spaced rudder shaft bases (2), the rudder shaft bases (2) are arranged inside the hull assembly (7), a cylinder assembly (6) is installed between the two rudder shaft bases (2), a limit position assembly (5) is installed on the cylinder assembly (6), and an upper slider (3) and a lower slider (4) spaced up and down are installed inside the cylinder assembly (6); the structure of the single wing assembly (1) is as follows: it comprises a wing plate (11), a rotating shaft (12) and a rotating shaft key (13), the wing plate (11) ) is arranged outside the hull assembly (7), the center of gravity of the wing plate (11) is located on the axis of the rotating shaft (12), the axis of the rotating shaft (12) is perpendicular to the middle longitudinal section of the hull assembly (7), the rotating shaft (12) runs through the entire cylinder assembly (6), and the bottom surface of the rotating shaft key (13) is fixedly connected to the rotating shaft (12) in the middle section of the cylinder assembly (6); the upper slider (3) and the lower slider (4) have the same structure, and the structure of the upper slider (3) is: it includes a No. 1 counterweight plate (31) arranged in the middle of the cylinder assembly (6), and No. 1 ball sliders (32) are respectively arranged on both sides of the No. 1 counterweight plate (31).

2. The passive anti-heeling device for emergency buoyancy according to claim 1, characterized in that: The structure of the hull assembly (7) is as follows: it comprises a light outer shell (71), a plurality of pressure-resistant cabins (72) are arranged inside the light outer shell (71), and a jettison (73) is arranged at the bottom of the hull.

3. The passive anti-heeling device for emergency buoyancy according to claim 1, characterized in that: The rotating shaft (12) is a rigid cylindrical shaft.

4. The passive anti-heeling device for emergency buoyancy according to claim 1, characterized in that: The rotating shaft key (13) is a rectangular rigid key with a rounded head, and the surface of the rotating shaft key (13) is provided with a rubber layer.

5. The passive anti-heeling device for emergency buoyancy according to claim 1, characterized in that: The thickness of the rotating shaft key (13) is the same as the gap between the upper slider (3) and the lower slider 4.

6. The passive anti-heeling device for emergency buoyancy according to claim 1, characterized in that: The structure of the oil cylinder assembly (6) is as follows: it comprises an oil cylinder shell (61), the bottom two sides of the oil cylinder shell (61) are provided with mounting ear plates, the mounting ear plates are fixed to the boat body by fasteners, the oil cylinder shell (61) is filled with lubricating oil, and the right side wall of the oil cylinder shell (61) is provided with two threaded through holes for mounting the limit assembly (5).

7. The passive anti-heeling device for emergency buoyancy according to claim 6, characterized in that: The oil cylinder shell (61) adopts a rectangular thin shell structure.

8. The passive anti-heeling device for emergency buoyancy according to claim 6, characterized in that: The structure of the limit assembly (5) is as follows: it includes a limit nut (51) installed in the threaded through hole, the limit nut (51) penetrates into the interior of the oil cylinder and is respectively pressed on the end faces of the upper slider (3) and the lower slider (4); it also includes a limit rope (52), one end of the limit rope (52) is connected to the front wall surface inside the oil cylinder shell (61), and the other end is connected to the front end surface of the upper slider (3).

9. The passive anti-heeling device for emergency buoyancy according to claim 8, characterized in that: The limiting rope (52) is a light and soft rigid rope.

10. A working process of a passive anti-heeling device dedicated for emergency buoyancy as claimed in claim 1, characterized in that: The process includes the following: When used as a stabilizer: The response heel angle is the same as the maximum allowable heel angle of the jettisoning device, and the heel angle of the submersible will not exceed the response heel angle of the passive anti-heeling device. The upper slider (3) and the lower slider (4) cannot break through the limit of the limit nut, and the rotating shaft (12) is continuously locked to limit the rotation, so as to maintain the wing plate (11) in a horizontal state, thereby realizing the function of stabilizing the wing; When used for emergency buoyancy: The passive anti-roll device is installed symmetrically on the left and right sides, and has the same effect in left and right roll; When the submersible is sinking rapidly with a large heel due to a hull breach or water ingress, if the heel exceeds the maximum allowable heel angle of the dumping mechanism, the dumping mechanism cannot dump the load. Since the response heel angle is the same as the maximum allowable heel angle of the dumping device, the passive anti-heel device is triggered to work. At this time, gravity drives the slider to slide and overcome the limit of the limit nut, partially releasing the rotation limit of the wing plate (11); the wing plate on the lifting side is turned to a vertical state and self-locked under the action of the diving current force; the wing plate (11) on the sinking side maintains a horizontal state, and the wing plates (11) on both sides generate anti-heeling hydrodynamic torque during the process of falling deep, reducing the heel and facilitating the implementation of dumping; After the load is jettisoned, during the process of the submersible floating up, the wing plate (11) on the sinking side is turned into a vertical state and locked under the action of the water flow force, thereby reducing the floating resistance and enhancing the stability of the posture.

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