High-pressure-resistance low-rigidity self-balancing type metal corrugated pipe

Abstract

The invention provides a high-pressure-resistance and low-rigidity self-balancing type metal corrugated pipe which comprises a flange plate, a corrugated pipe body, a first ring body and a second ring body. The two first ring bodies are arranged at the two ends of the corrugated pipe in a sleeving mode respectively, the surfaces, facing the wave hills, of the first ring bodies are provided with profiling faces, and the profiling faces are matched with the surfaces of one sides of the wave hills; the second ring bodies are arranged between the adjacent wave hills in a sleeving mode, and the two side faces, facing the adjacent wave hills, of the second ring bodies are also arranged to be profiling faces; when the corrugated pipe is in a loose state, a gap is reserved between the profiling surface and the side surface of the wave hill; when the corrugated pipe is in a compressed state, the two side faces of each wave hill are tightly attached to the two adjacent profiling faces. The low-rigidity characteristic of the corrugated pipe is utilized, so that the corrugated pipe can absorb vibration and impact force from the external environment or operation of an internal system, and the influence of vibration on the structure and equipment of the underwater vehicle is reduced; and under the extreme working condition, the corrugated pipe is compressed to enable the ring bodies sleeved on the corrugated pipe to abut against each other, so that the corrugated pipe has higher rigidity and higher safety.

Description

Technical Field

[0001] The present invention relates to the technical field of bellows, in particular to a high-pressure-resistant, low-rigidity, self-balancing metal bellows. Background Art

[0002] The design and manufacture of underwater vehicles (AUVs) are highly complex and technology-intensive. They must operate in extreme environments, including high pressure, low temperatures, and seawater corrosion. These requirements place stringent demands on every aspect of the AUV, including its hull structure, power system, control system, and piping.

[0003] Piping systems play a crucial role in underwater vehicles. They transport media such as water, gas, and liquids, connecting compartments and equipment, and must withstand the high pressure and deformation of deep-sea environments. While traditional rigid pipes offer strength, their high stiffness makes them less adaptable to the deformation and vibration of underwater vehicles, and they are susceptible to rupture or damage from water pressure. Therefore, it is necessary to develop a new type of piping system to meet the complex environmental demands of underwater vehicles. High-pressure, low-rigidity bellows are an innovative technology that has emerged in response to this demand.

[0004] High pressure resistance means that even in extreme deep-sea conditions, the bellows will not rupture or be damaged by external pressure. Meanwhile, low stiffness means that the bellows can easily deform under external forces. This allows the bellows to withstand a certain degree of displacement and bending without damage, thereby providing better connection and sealing performance. The present invention aims to achieve a bellows that balances the ability to withstand high external water pressure with sufficiently low stiffness by optimizing the bellows' corrugation shape, material, and design. Summary of the Invention

[0005] In view of this, the present invention proposes a high-pressure-resistant, low-rigidity self-balancing metal bellows to solve the problem that there is currently no bellows that can both withstand high external water pressure and maintain sufficiently low rigidity.

[0006] The technical solution of the present invention is achieved as follows: the present invention provides a high-pressure-resistant, low-rigidity self-balancing metal bellows, comprising a flange plate, a bellows, a first ring body and a second ring body; the two flange plates are arranged at intervals; the bellows is arranged between the two flange plates, the two ends of the bellows extend toward the two flange plates, and a plurality of corrugated hillocks are arranged at intervals on the outer peripheral wall of the bellows; the two first ring bodies are respectively sleeved on the two ends of the bellows and respectively abut against the two flange plates, and the surface of the first ring body facing the corrugated hillock is provided with a contoured surface, which cooperates with one side surface of the corrugated hillock; a plurality of second ring bodies are arranged at intervals along the axial direction of the bellows, each second ring body is sleeved between adjacent corrugated hillocks, and the two side surfaces of the second ring body facing the adjacent corrugated hillocks are also provided with contoured surfaces; when the bellows is in a relaxed state, a gap is left between the contoured surface and the side surfaces of the corrugated hillock; when the bellows is in a compressed state, the two side surfaces of the corrugated hillock are tightly attached to the two adjacent contoured surfaces.

[0007] On the basis of the above technical solution, preferably, the outer edge of the first ring body is provided with a flange, which protrudes and extends toward the second ring body; the outer edge of the second ring body is also provided with a flange, which protrudes and extends toward the adjacent second ring body or the first ring body; when the bellows is in a relaxed state, adjacent flanges are arranged at intervals.

[0008] More preferably, before the bellows is compressed to its limit, adjacent flanges abut against each other.

[0009] More preferably, when the bellows is in a relaxed state, the spacing between adjacent contoured surfaces is greater than the axial length of the corrugated tube, and the spacing between adjacent flanges is less than the axial length of the corrugated tube.

[0010] On the basis of the above technical solution, preferably, the inner edges of the first ring body and the second ring body abut against the outer wall of the corrugated tube, and the inner edges of the first ring body and the second ring body are chamfered.

[0011] On the basis of the above technical solution, preferably, the wall of the corrugated tube is a layered structure, and the number of layers of the wall of the corrugated tube is two to four.

[0012] On the basis of the above technical solution, preferably, the number of corrugated tubes is four to eight.

[0013] On the basis of the above technical scheme, preferably, it also includes a first movable plate, a second movable plate, a first sliding rod and a second sliding rod, the first movable plate and the second movable plate are arranged at intervals between two flange plates; three bellows are respectively arranged between the flange plate and the first movable plate, between the first movable plate and the second movable plate, and between the second movable plate and the other flange plate; a number of first sliding rods are axially arranged outside the bellows, one end of the first sliding rod is arranged on one of the flange plates, and the other end of the first sliding rod passes through the first movable plate and is arranged on the second movable plate; a number of second sliding rods are axially arranged outside the bellows, the second sliding rod is staggered with the first sliding rod, one end of the second sliding rod is arranged on another flange plate, and the other end of the second sliding rod passes through the second movable plate and is arranged on the first movable plate.

[0014] More preferably, the diameter of the bellows located between the first movable plate and the second movable plate is larger than the diameters of the other two bellows, and the diameters of the other two bellows are the same.

[0015] More preferably, the thickness of the flange plate is greater than the thickness of the first movable plate or the second movable plate, and the thickness of the first movable plate is the same as that of the second movable plate.

[0016] The high-pressure-resistant, low-rigidity self-balancing metal bellows of the present invention has the following advantages over the prior art:

[0017] Beneficial effects:

[0018] (1) The present invention sets a reinforcement ring between the corrugated tube's ridges. Under normal working conditions or low internal pressure conditions, the corrugated tubes will not be in complete contact with the reinforcement rings. The low stiffness of the bellows makes the tube as a whole have better vibration isolation performance. The low stiffness of the bellows itself enables it to absorb vibration and impact from the external environment or the operation of the internal system, which helps to reduce the impact of vibration on the underwater vehicle structure and equipment, extend its service life, and improve the comfort of the crew; under extreme working conditions, the bellows are compressed and the ring bodies mounted on it abut against each other, making the bellows have higher stiffness and greater safety. Compared with traditional piping systems, the high-pressure-resistant, low-rigidity bellows of the present invention are lighter and can provide sufficient strength and pressure resistance. Due to the flexibility and plasticity of the bellows, they can be more flexibly arranged and installed inside the underwater vehicle, adapting to complex hull structures and system layouts. This allows designers to better optimize the internal space utilization of the underwater vehicle and simplify the installation and maintenance of the system.

[0019] (2) The present invention uses a sliding rod and a movable plate to form a three-section structure of the bellows, wherein the first and last sections are working sections and the middle section is a balancing section. When the bellows is in a compressed state, the elastic performance of the middle balancing section can balance the stiffness changes of the working sections at both ends, thereby achieving the purpose of low-stiffness self-balancing adjustment of the bellows. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0021] Figure 1 A perspective view of a metal bellows according to the present invention;

[0022] Figure 2 An axial cross-sectional view of the metal bellows of the present invention;

[0023] Figure 3 is a three-dimensional diagram of the first ring body and the second ring body of the present invention;

[0024] Figure 4 This is a stress cloud diagram of the metal bellows of the present invention under an internal pressure of 2 MPa;

[0025] Figure 5 The stress cloud diagram of the metal bellows of the present invention under an internal pressure of 10 MPa;

[0026] Figure 6 This is a stress cloud diagram of the metal bellows of the present invention under an internal pressure of 30 MPa;

[0027] Figure 7 The force-displacement curve of the metal bellows of the present invention when axially compressed by 15 mm under an internal pressure of 2 MPa;

[0028] Figure 8 The force-displacement curve of the metal bellows of the present invention when axially compressed by 15 mm under an internal pressure of 10 MPa;

[0029] Figure 9 This is a comparison diagram of force-displacement curves of the metal bellows of the present invention having different numbers of wave hills and being subjected to different axial compression conditions.

[0030] In the figure: 1, flange plate; 2, bellows; 21, corrugated tube; 3, first ring body; 31, flange; 301, contoured surface; 4, second ring body; 5, first movable plate; 6, second movable plate; 7, first slide bar; 8, second slide bar. DETAILED DESCRIPTION

[0031] The following will be combined with the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0032] like Figure 1 As shown, combined Figure 2 The present invention provides a high-pressure-resistant, low-rigidity, self-balancing metal bellows, comprising a flange plate 1, a bellows 2, a first ring body 3, and a second ring body 4.

[0033] The two flange plates 1 are spaced apart. The flange plates 1 are a mechanical interface between the corrugated pipe and other pipes or equipment components. They are mainly used in piping systems to enable the corrugated pipe to be safely and reliably connected to other pipes or equipment.

[0034] The bellows 2 is disposed between the two flange plates 1, with both ends of the bellows 2 extending toward the two flange plates 1. A plurality of corrugated hillocks 21 are spaced apart on the outer circumference of the bellows 2. The bellows 2 can be made of rubber or metal. The ends of the bellows 2 can be welded to the flange plates 1.

[0035] The two first ring bodies 3 are respectively sleeved on both ends of the corrugated tube 2 and respectively abut against the two flange plates 1. The surface of the first ring body 3 facing the corrugated hillock 21 is provided with a contoured surface 301, which matches one side surface of the corrugated hillock 21.

[0036] Several second ring bodies 4 are spaced apart axially along the bellows 2, each nested between adjacent corrugations 21. The two sides of the second ring bodies 4 facing adjacent corrugations 21 are also configured with contoured surfaces 301. The first and second ring bodies 3 and 4 are essentially reinforcement rings for the bellows. To facilitate installation, each reinforcement ring is formed by two semicircular rings with ears connected by bolts.

[0037] The biggest difference between the bellows of this embodiment and conventional bellows lies in the state of the reinforcement ring. The reinforcement ring of a conventional bellows is already in full contact with the wall of the bellows 2 when there is no internal pressure. Therefore, the stiffness difference between conventional bellows under high internal pressure and low internal pressure conditions is relatively low. However, the contact state between the reinforcement ring and the wall of the bellows 2 in the bellows proposed in this embodiment changes with the change of internal pressure. Specifically, when the bellows 2 is in a relaxed state, there is a gap between the contoured surface 301 and the side of the corrugated hillock 21; when the bellows 2 is in a compressed state, the two side surfaces of the corrugated hillock 21 are tightly attached to the two adjacent contoured surfaces 301. In this embodiment, the thickness of the second ring body 4 will be smaller than the gap width between the adjacent corrugated hillocks 21. Therefore, when the bellows 1 is under a lower internal pressure load, for example Figure 4As shown, the bellows 2 is under an internal pressure of 2MPa. At this time, the compression of the bellows 2 is small, the deformation of the corrugated hillock 21 is small, and the stress is also low, which is less than the yield strength of the material used. The bellows 2 will not be damaged. Since there is a certain gap between the reinforcing ring and the corrugated hillock 21, and there is no complete contact with the bellows 2, the reinforcing ring and the bellows 1 are in a separated state, and the bellows 2 has a small rigidity. The reinforcing ring does not play a protective role at this time. Figure 4 From the stress diagram, it can be found that the stiffening ring is not completely in contact with the corrugated hill 21 and the stiffness of the whole model will not be large. However, as the internal pressure increases, the deformation of the corrugated hill 21 increases. For example, Figure 5 As shown, when the bellows 2 is under an internal pressure of 10 MPa, the side of the corrugated hillock 21 will partially contact the contoured surface 301, and the stiffness of the bellows 2 will increase slightly. However, the stress at this time still does not reach the yield strength of the material, and the bellows 2 will not be damaged. Therefore, the bellows 2 can still have a low stiffness while ensuring its safety. The reinforcement ring does not need to play a protective role at this time. Figure 5 From the stress diagram, it can be found that the stiffness of the overall model will not be large even if the reinforcing ring is not in full contact with the bellows. Furthermore, when the internal pressure of the bellows 2 reaches the bursting pressure level, for example Figure 6 As shown, when the bellows 2 is under an internal pressure of 30 MPa, the side of the corrugated hillock 21 will partially contact the contoured surface 301, and the side of the corrugated hillock 21 will completely contact the contoured surface 301. The reinforcing ring can effectively limit the large deformation of the corrugated hillock 21, enhance the structural strength of the bellows 2, improve its ability to withstand pressure, and improve its durability and stability. Figure 6 The stress diagram shows that the stiffness of the overall model is already high due to the full contact of the reinforcement ring. The reinforcement ring has a significant impact on the displacement compensation ability, pressure resistance, and stiffness of the overall prototype during the entire loading process.

[0038] exist Figure 3 In the preferred embodiment shown, the outer edge of the first ring body 3 is provided with a flange 31, which protrudes and extends toward the second ring body 4. The outer edge of the second ring body 4 is also provided with a flange 31, which protrudes and extends toward the adjacent second ring body 4 or first ring body 3. When the bellows 2 is in the relaxed state, adjacent flanges 31 are spaced apart. The flanges 31 surround the corrugation mound 21 from the outside, so that the two adjacent contoured surfaces 301 form a cavity similar to a horizontal U-shaped cavity that covers the horizontal U-shaped corrugation mound 21. This ensures that the contoured surfaces 301 have sufficient contact area with the surface of the corrugation mound 21 under high internal pressure conditions.

[0039] exist Figure 3In a preferred embodiment shown, adjacent flanges 31 abut against each other before the bellows 2 is compressed to its limit. The flanges 31 act as limiters at this time, and the abutment of adjacent flanges 31 prevents the bellows 2 from further deforming and bursting.

[0040] exist Figure 2 In the preferred embodiment shown, when the bellows 2 is in a relaxed state, the distance between adjacent contoured surfaces 301 is greater than the axial length of the corrugated tube 21, while the distance between adjacent flanges 31 is less than the axial length of the corrugated tube 21. Because the second ring body 4 is relatively thin, when the bellows 2 is in a relaxed state, the second ring body 4 overlaps the corrugated tube 21 below due to its own weight. At this time, there is a large distance between the upward-facing contoured surface 301 of the second ring body 4 and the corrugated tube 21 above it.

[0041] exist Figure 2 In a preferred embodiment shown, the inner edges of the first ring body 3 and the second ring body 4 abut against the outer wall of the bellows 2, and the inner edges of the first ring body 3 and the second ring body 4 are chamfered to avoid friction damage between the outer wall of the bellows 2 and the inner edges of the first ring body 3 and the second ring body 4 during the deformation of the corrugated tube 21.

[0042] exist Figure 2 In a preferred embodiment shown, the wall of the bellows 2 is a layered structure, and the number of wall layers of the bellows 2 is two to four. The increase in the thickness of the bellows 2 will have a certain degree of impact on the change in the stiffness of the bellows 2. For example, when the bellows 2 has four wall layers and is subjected to a certain internal pressure, the change in stiffness will usually be greater than the change in stiffness when the bellows 2 has two wall layers and is subjected to the same internal pressure. However, due to the design of the reinforcement ring, the effect of the change in the number of wall layers of the bellows 2 on the bellows device of this embodiment can be basically ignored. When the bellows 2 is made of metal, titanium alloy can be used; the first ring body 3 and the second ring body 4 are also made of titanium alloy. The flange plate 1 is made of steel.

[0043] exist Figure 2 In a preferred embodiment shown, the number of the corrugated tubes 21 is four to eight. The change in the number of the corrugated tubes 21 will affect the self-balancing performance of the stiffness of the corrugated tubes of this embodiment. Figure 9As shown, when the bellows 2 has four corrugations 21, the internal pressure of the bellows 2 gradually increases, but its axial displacement increases slowly; when the bellows 2 has eight corrugations 21, the internal pressure of the bellows 2 gradually increases, and its axial displacement increases significantly; and when the bellows 2 has four corrugations 21, and its inner diameter is 50 mm and 100 mm respectively, the bellows 2 is subjected to the same internal pressure and gradually increases, but the difference in the axial displacement of the bellows 2 in the two cases is not obvious. Therefore, it can be seen that the number of corrugations 21 has a greater influence on the stiffness of the bellows 2, and the more corrugations 21 there are, the greater the stiffness. However, the change in the inner diameter of the bellows 2 has little effect on the performance. Therefore, in practical applications, the number of corrugations 21, the inner diameter of the tube, and the size of the reinforcement ring of the bellows can be designed according to the actual needs of the project.

[0044] exist Figure 1 and Figure 2 A preferred embodiment shown in the figure further includes a first movable plate 5 , a second movable plate 6 , a first sliding rod 7 and a second sliding rod 8 .

[0045] The first movable plate 5 and the second movable plate 6 are spaced apart and arranged between the two flange plates 1 .

[0046] The three bellows 2 are respectively arranged between the flange plate 1 and the first movable plate 5 , between the first movable plate 5 and the second movable plate 6 , and between the second movable plate 6 and another flange plate 1 .

[0047] A plurality of first slide bars 7 are axially arranged around the bellows 2 outside the bellows 2 , one end of the first slide bar 7 is set on one of the flange plates 1 , and the other end of the first slide bar 7 passes through the first movable plate 5 and is set on the second movable plate 6 .

[0048] Several second slide bars 8 are arranged axially around the bellows 2 and outside the bellows 2. They are offset from the first slide bars 7. One end of each second slide bar 8 is attached to the other flange plate 1, while the other end passes through the second movable plate 6 and is attached to the first movable plate 5. Each slide bar is bolted to the movable plate and flange plate 1. The slide bars ensure smooth sliding of the movable plate during installation and use, reducing friction and improving efficiency. Furthermore, the slide bars must be designed to withstand the equipment's motion loads and external impacts, preventing deformation or jamming that could affect the overall performance of the device.

[0049] The three-section self-balancing bellows in underwater vehicles needs to play its displacement and deformation coordination ability, and can maintain low stiffness while bearing internal pressure and axial tension and compression loads. Figure 7This is the force-displacement curve of the axial compression deformation of the bellows under an internal pressure of 2 MPa. It can be seen that under low internal pressure (2 MPa), the reinforcement ring that is completely out of contact with the corrugated hill 21 still maintains a low stiffness when axially compressed by 15 mm. The stiffness does not begin to increase sharply until the reinforcement ring is in full contact with the bellows. Figure 8 Figure 2 shows the force-displacement curve of the bellows under axial compression at an internal pressure of 10 MPa. It can be seen that under a moderate internal pressure (10 MPa), the partially contacted reinforcement ring maintains a low stiffness when subjected to an axial compression of approximately 13 mm. The stiffness only increases dramatically when the reinforcement ring is in full contact with the bellows. Therefore, the metal bellows of this embodiment can not only be used to isolate and connect underwater vehicle compartments, but can also serve as connecting pipes for underwater equipment, transporting media such as water, gas, and liquids. Its flexibility also enables it to provide shock absorption and energy absorption when the underwater vehicle is subjected to external impact or vibration, protecting the safety of the equipment and personnel within the underwater vehicle. Furthermore, the bellows' flexibility and lightweight design make its installation more flexible and convenient, while also reducing maintenance costs. Compared to traditional rigid pipes, bellows are more convenient and quick to install and maintain, helping to improve the operational efficiency of underwater vehicles.

[0050] exist Figure 2 In a preferred embodiment shown, the diameter of the bellows 2 located between the first movable plate 5 and the second movable plate 6 is larger than the diameters of the other two bellows 2, and the diameters of the other two bellows 2 are the same. Specifically, the overall model of the bellows device can be divided into a working section and a balancing section, wherein the bellows 2 at the upper and lower ends are the working sections, and the middle section is the balancing section; the bellows 2 in the working section have the same dimensions, wherein the inner diameter is 50mm, the straight side length is 15mm, the height of the corrugated hillock 21 is 16mm, the radius of the outer wave is 8.2mm, and the number of waves in each section is 4. The design of the corrugated hillock 21 affects the deformation ability of the bellows 2 when subjected to force and pressure changes. These parameters optimize the elasticity and deformation ability of the bellows 2 during operation, thereby achieving higher performance and reducing system To reduce vibration and noise in the system, a reasonable waveform design helps to improve the flexibility and ductility of the bellows 2; the inner and outer walls of the tube are composed of four layers, each 0.6mm thick. This design allows the bellows 2 to have higher pressure bearing capacity and durability. Under the action of pressure fluctuations, the outer and inner waves of the bellows 2 can support each other, avoiding the risk of single-layer bellows 2 being easily broken or fatigued under high pressure; the inner diameter of the balancing section bellows 2 is 76.8mm, and the other dimensions are the same as the working section; the height of the bellows 2 at both ends of the working section and the middle balancing section is 142mm. The working section bellows 2 are the same size and smaller, which helps to improve the rigidity and control accuracy of the system; while the balancing section bellows 2 have a larger diameter, which helps to enhance the device's ability to adjust to pressure changes during operation and ensure the stability and response speed of the system.

[0051] exist Figure 2In a preferred embodiment, the thickness of the flange plate 1 is greater than that of the first movable plate 5 or the second movable plate 6. The first movable plate 5 and the second movable plate 6 are of equal thickness. This ensures uniform force distribution during the movement of the bellows device, avoids deformation or localized stress concentration caused by thickness differences, and ensures structural symmetry and stability. Specifically, the two flange plates 1 are 40 mm thick, and the two movable plates are 15 mm thick. There are eight slide rods, each measuring 374 mm in length and 15 mm in diameter, respectively. The thickened flange plate 1 enhances the device's rigidity and sealing performance. Especially when subjected to high external pressure, the thick flange plate 1 effectively distributes and withstands the pressure, reducing the risk of seal failure. The thinner thickness of the movable plates provides greater flexibility during assembly and movement. Through the appropriate thickness differences and slide rod design, the entire device maintains high-precision adjustment during operation. In particular, during the deformation of the bellows 2, the deformation range is effectively controlled and limited, ensuring long-term stable operation without malfunction or performance degradation.

[0052] 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, improvements, etc. made within the spirit and principles of the present invention should be included in the scope of protection of the present invention.

Claims

1. A high-pressure-resistant, low-rigidity, self-balancing metal bellows, characterized by: It comprises a flange plate (1), a bellows (2), a first ring body (3) and a second ring body (4); The two flange plates (1) are spaced apart; The bellows (2) is arranged between the two flange plates (1), with both ends of the bellows (2) extending toward the two flange plates (1), and a plurality of corrugated hillocks (21) are arranged at intervals on the outer peripheral wall of the bellows (2); The two first ring bodies (3) are respectively sleeved on the two ends of the corrugated pipe (2) and respectively abutted against the two flange plates (1); the surface of the first ring body (3) facing the corrugated tube (21) is provided with a contoured surface (301), and the contoured surface (301) is matched with one side surface of the corrugated tube (21); A plurality of second ring bodies (4) are arranged at intervals along the axial direction of the corrugated tube (2), each of the second ring bodies (4) is sleeved between adjacent corrugated hillocks (21), and two side surfaces of the second ring body (4) facing the adjacent corrugated hillocks (21) are also provided as contoured surfaces (301); When the bellows (2) is in a relaxed state, a gap is left between the contoured surface (301) and the side surface of the corrugated hillock (21); when the bellows (2) is in a compressed state, the two side surfaces of the corrugated hillock (21) are in close contact with two adjacent contoured surfaces (301).

2. The high-pressure-resistant, low-rigidity, self-balancing metal bellows according to claim 1, characterized in that: The outer edge of the first ring body (3) is provided with a flange (31), and the flange (31) protrudes and extends toward the second ring body (4); The outer edge of the second ring body (4) is also provided with a flange (31), and the flange (31) protrudes and extends toward the adjacent second ring body (4) or the first ring body (3); When the bellows (2) is in a relaxed state, adjacent flanges (31) are arranged at intervals.

3. The high-pressure-resistant, low-rigidity, self-balancing metal bellows according to claim 2, characterized in that: Before the bellows (2) is compressed to its limit, adjacent flanges (31) abut against each other.

4. The high-pressure-resistant, low-rigidity, self-balancing metal bellows according to claim 2, characterized in that: When the bellows (2) is in a relaxed state, the spacing between adjacent contoured surfaces (301) is greater than the axial length of the corrugated tube (21) along the bellows (2), and the spacing between adjacent flanges (31) is less than the axial length of the corrugated tube (21) along the bellows (2).

5. The high-pressure-resistant, low-rigidity, self-balancing metal bellows according to claim 1, characterized in that: The inner edges of the first ring body (3) and the second ring body (4) abut against the outer wall of the corrugated tube (2), and the inner edges of the first ring body (3) and the second ring body (4) are rounded.

6. The high-pressure-resistant, low-rigidity, self-balancing metal bellows according to claim 1, characterized in that: The wall of the corrugated pipe (2) is a layered structure, and the number of layers of the wall of the corrugated pipe (2) is two to four.

7. The high-pressure-resistant, low-rigidity, self-balancing metal bellows according to claim 1, characterized in that: The number of the corrugated tubes (21) is four to eight.

8. The high-pressure-resistant, low-rigidity, self-balancing metal bellows according to claim 1, characterized in that: It also includes a first movable plate (5), a second movable plate (6), a first slide bar (7) and a second slide bar (8), The first movable plate (5) and the second movable plate (6) are spaced apart and arranged between the two flange plates (1); The three bellows (2) are respectively arranged between the flange plate (1) and the first movable plate (5), between the first movable plate (5) and the second movable plate (6), and between the second movable plate (6) and another flange plate (1); A plurality of first sliding rods (7) are axially arranged around the bellows (2) and outside the bellows (2), one end of the first sliding rod (7) is arranged on one of the flange plates (1), and the other end of the first sliding rod (7) passes through the first movable plate (5) and is arranged on the second movable plate (6); A plurality of second slide bars (8) are axially arranged around the bellows (2) outside the bellows (2), the second slide bars (8) and the first slide bars (7) are staggered, one end of the second slide bar (8) is arranged on another flange plate (1), and the other end of the second slide bar (8) passes through the second movable plate (6) and is arranged on the first movable plate (5).

9. The high-pressure-resistant, low-rigidity, self-balancing metal bellows according to claim 8, characterized in that: The diameter of the bellows (2) located between the first movable plate (5) and the second movable plate (6) is larger than the diameters of the other two bellows (2), and the diameters of the other two bellows (2) are the same.

10. The high-pressure-resistant, low-rigidity, self-balancing metal bellows according to claim 8, characterized in that: The thickness of the flange plate (1) is greater than the thickness of the first movable plate (5) or the second movable plate (6), and the thickness of the first movable plate (5) and the second movable plate (6) are the same.

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