Deep sea power push rod

Abstract

The present application relates to a kind of deep-sea power push rod, it relates to deep-sea equipment technical field, comprising: cylinder unit, stem;The stem and cylinder unit are slidably connected using dynamic sealing mode;The cylinder unit includes: the main cylinder of two ends opening, the guide module sealedly connected with the front end of main cylinder, the switch control module sealedly connected with the rear end of main cylinder;The stem cleaning structure is provided at the end of the guide module away from main cylinder;Along the axial direction of guide module, the stem cleaning structure relative two sides are communicated with external deep-sea environment;The switch control module is used to control the communication between the inside of cylinder unit and external deep-sea environment, to control the entry of external seawater to push the stem to extend out.The deep-sea power push rod of the present application is simple and reliable in structure, and can realize reliable power output in deep-sea environment only by relying on the pressure difference between inside and outside.

Description

Technical Field

[0001] This invention relates to the field of deep-sea equipment technology, and in particular to a deep-sea power push rod. Background Technology

[0002] In the process of deep-sea exploration and development, the field of deep-sea equipment engineering technology plays a crucial role. Deep-sea power push rods, as a key linear power output device, are widely used in various deep-sea environments. Their common forms are mainly electric and hydraulic, relying on underwater electric motors or underwater hydraulic motors for power, respectively.

[0003] However, the deep-sea environment is extremely complex, with high pressure being one of its most prominent characteristics. In such an environment, to ensure that the power unit can operate normally and output sufficient power, the design of the device often becomes extremely complex, while energy consumption is also relatively large.

[0004] For drive systems powered by electric motors, high thrust output requires pressure compensation devices due to the high pressure in the deep sea. This not only complicates the system structure but also increases the strength requirements, leading to a significant increase in the overall size and weight of the device. Generally, the thrust demand can only be met under medium to high pressure conditions, which places higher demands on the battery's output power. For example, in deep-sea oil and gas extraction and other operations requiring high thrust, the internal pressure compensation structure of the electric motor drive system needs to be meticulously designed to overcome the high-pressure environment and provide sufficient power. Furthermore, to ensure structural strength, the selection of materials and processing techniques are more stringent, undoubtedly increasing the system's complexity and cost. Moreover, higher power consumption means a larger capacity battery is needed to maintain operation, further limiting the device's endurance and overall performance.

[0005] Hydraulic drive systems, while offering advantages in achieving high thrust, are extremely complex. They require not only a pumping system to provide stable hydraulic power but also intricate oil circuit designs to ensure proper distribution and flow of hydraulic oil. Furthermore, they rely heavily on an electronic control system for precise process control. The coordinated operation of these components results in a significant space and weight footprint, leading to lower system reliability. For example, in the complex terrain and environment of the deep sea, hydraulic pipelines are susceptible to impacts and corrosion. Oil leaks or other malfunctions not only make repairs difficult but can also cause the entire power unit to fail, severely impacting deep-sea operations.

[0006] Furthermore, the deep-sea working environment is characterized by low temperatures, high corrosiveness, and a high abundance of microorganisms, posing numerous challenges to the normal operation of deep-sea power push rods. On one hand, the high environmental pressure in the deep sea puts immense strain on the piston rod seal, making it highly susceptible to failure. Once the seal fails, seawater and the abundant microorganisms can penetrate, causing wear, jamming, and other problems. On the other hand, the piston rod extends outwards during operation, and its outer surface is easily contaminated by external dirt or microorganisms, leading to operational difficulties and affecting overall performance.

[0007] It is evident that existing deep-sea powered actuators, whether electric or hydraulic, have limitations in handling the complex deep-sea environment. Developing a powered actuator with a relatively simple structure, low energy consumption, high reliability, and adaptability to the harsh deep-sea environment has become a crucial problem urgently needing to be solved in the field of deep-sea equipment engineering technology. Summary of the Invention

[0008] The technical problem to be solved by the present invention is to provide a deep-sea power push rod.

[0009] To achieve the above-mentioned objectives, the present invention provides a deep-sea power push rod, comprising: a cylinder unit and a rod body;

[0010] The rod body and the cylinder body unit are slidably connected by a dynamic sealing method;

[0011] The cylinder unit includes: a main cylinder with openings at both ends, a guide module sealed to the front end of the main cylinder, and a switch control module sealed to the rear end of the main cylinder;

[0012] The guide module is equipped with a rod-shaped cleaning structure at the end away from the main cylinder.

[0013] Along the axial direction of the guide module, the rod cleaning structure is in communication with the external deep-sea environment on both sides.

[0014] The switch control module is used to control the connection between the inside of the cylinder unit and the external deep-sea environment, so as to control the entry of external seawater to push the rod to extend.

[0015] According to one aspect of the invention, the end of the rod extending outside the cylinder unit is the working end, and the end of the rod inside the cylinder unit is the piston end;

[0016] The end area of ​​the piston end is greater than the end area of ​​the working end;

[0017] When the switch control module is turned on, the rod body outputs power based on the different pressure differences at its two ends.

[0018] According to one aspect of the present invention, the rod cleaning structure includes: a retaining ring structure and a flexible cleaning ring mounted on the retaining ring structure;

[0019] The inner side of the retaining ring structure is provided with a first annular groove, the radial outer side of the flexible cleaning ring is embedded in the first annular groove, and the radial inner side of the flexible cleaning ring is in contact with the radial outer side of the rod.

[0020] The retaining ring structure is provided with a water-permeable channel for connecting the two axial sides of the retaining ring structure, and the water-permeable channel is offset from the first annular groove along the radial direction of the retaining ring structure.

[0021] According to one aspect of the present invention, the retaining ring structure is an integral ring structure, or the retaining ring structure is a ring structure composed of multiple coaxial ring bodies stacked sequentially.

[0022] According to one aspect of the invention, the minimum radial dimension of the inner radial surface of the retaining ring structure is greater than the radial dimension of the corresponding position of the rod.

[0023] According to one aspect of the present invention, the guiding module further includes: a hollow guiding cylinder, a first sealing ring, a first retaining ring, and a guiding sleeve disposed within the guiding cylinder;

[0024] Along the direction from the front end to the rear end of the cylinder unit, the hollow portion of the guide cylinder is sequentially provided with a first hollow portion, a second hollow portion, and a third hollow portion;

[0025] The first sealing ring and the first retaining ring are disposed in the first hollow part, and the first retaining ring abuts against the first sealing ring and the guide cylinder on both axial sides respectively;

[0026] The guide sleeve is installed in the third hollow section using an interference fit.

[0027] According to one aspect of the invention, a piston structure is provided at the piston end of the rod;

[0028] The piston structure has a second annular groove on its outer side, and a second sealing ring and a second retaining ring are fitted in the second annular groove.

[0029] The two opposite sides of the second retaining ring abut against the second sealing ring and the piston structure, respectively.

[0030] According to one aspect of the invention, an anti-wear ring is nested on the outer side of the piston structure.

[0031] According to one aspect of the present invention, both the first sealing ring and the second sealing ring are U-shaped sealing rings, and the material used is fluororubber;

[0032] The first retaining ring and the second retaining ring are made of polytetrafluoroethylene;

[0033] The anti-wear ring is made of phenolic resin reinforced with cotton fabric.

[0034] According to one aspect of the present invention, the switch control module includes: an end cap, a throttle valve, and a control switch;

[0035] The end cap has an input channel running through its opposite sides at its center;

[0036] The throttle valve and control switch are installed at opposite ends of the input channel, wherein the throttle valve is arranged within the cylinder block unit;

[0037] The control switch is one of a solenoid valve switch or a pressure rupture disc.

[0038] According to one aspect of the present invention, the deep-sea power push rod of the present invention has a simple and reliable structure, and can achieve reliable power output in the deep-sea environment by relying solely on the internal and external pressure difference.

[0039] According to one aspect of the present invention, the deep-sea power push rod of the present invention meets the application requirements of various thrust scenarios in the deep sea, and has the advantages of lower cost and easier implementation, especially for high thrust requirements.

[0040] According to one aspect of the present invention, the deep-sea power push rod can achieve its power output effect without an additional power source. Compared with traditional electric and hydraulic drive methods, it has more convenient performance and greater adaptability to the deep-sea environment. Furthermore, by eliminating the need for a complex external power source, the overall load of the deep-sea power push rod is lower, which is more beneficial for increasing the effective load of the device employing this solution.

[0041] According to one aspect of the present invention, the rod cleaning structure effectively removes contaminants adhering to the rod during operation, which is beneficial for ensuring the reliable and stable operation of the solution. Furthermore, the rod cleaning structure effectively prevents external contaminants from affecting the sealing ring, enabling the solution to maintain a more durable sealing performance in deep-sea environments, thus improving its long-term operational capability. Attached Figure Description

[0042] Figure 1 This is a structural diagram of the deep-sea power push rod of the present invention;

[0043] Figure 2 This is a structural diagram of the guiding module of the present invention;

[0044] Figure 3 This is a structural diagram of the first retaining ring portion of the present invention;

[0045] Figure 4 This is a structural diagram of the second retaining ring portion of the present invention;

[0046] Figure 5 This is a structural diagram of the flexible cleaning ring of the present invention;

[0047] Figure 6 This is a structural diagram of the guide cylinder of the present invention;

[0048] Figure 7 This is a structural diagram of the first sealing ring of the present invention;

[0049] Figure 8 This is a structural diagram of the guide sleeve of the present invention;

[0050] Figure 9 This is a structural diagram of the piston structure of the present invention;

[0051] Figure 10 This is a structural diagram of the throttle valve of the present invention.

[0052] In the diagram, 1-cylinder unit, 2-rod, 11-main cylinder, 12-guide module, 13-switch control module, 121-rod cleaning structure, 1211-retaining ring structure, 1212-flexible cleaning ring, 1211a-first annular groove, 1211b-water permeable channel, 1211c-first retaining ring section, 1211d-second retaining ring section, 1212a-annular cleaning section, 1212b-annular receiving groove, 12a-guide cylinder, 122-first sealing ring, 123-first retaining ring, 124-guide sleeve, 21-piston structure, 21a-second annular groove, 21b-second sealing ring, 21c-second retaining ring, 21d-anti-wear ring, 131-end cap, 132-throttle valve, 133-control switch. Detailed Implementation

[0053] In describing embodiments of the present invention, the terms "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer" express orientations or positional relationships based on the orientations or positional relationships shown in the relevant drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, the above terms should not be construed as limitations on the present invention.

[0054] The present invention will now be described in detail with reference to the accompanying drawings and specific embodiments. The embodiments cannot be described in detail here, but the embodiments of the present invention are not limited to the following embodiments.

[0055] like Figure 1As shown, according to one embodiment of the present invention, a deep-sea power push rod includes: a cylinder unit 1 and a rod 2; wherein, based on the pressure difference between the inside and outside, the rod 2 can extend outward along the cylinder unit 1 to achieve the effect of thrust output; in this embodiment, the rod 2 and the cylinder unit 1 are slidably connected by a dynamic sealing method to effectively ensure the overall sealing performance and achieve reliable and stable power output. Furthermore, the cylinder unit 1 is the outer shell of the entire deep-sea power push rod, specifically including: a main cylinder 11 with openings at both ends, a guide module 12 sealed to the front end of the main cylinder 11, and a switch control module 13 sealed to the rear end of the main cylinder 11; wherein, one end of the rod 2 is located inside the cylinder unit 1 to achieve a sliding connection with the cylinder unit 1, and divides the internal space of the cylinder unit 1 into two chambers, front and rear. Thus, by controlling the opening and closing of the rear chamber, external deep-sea seawater is filled into it to apply pressure to the end of the rod 2; the other end of the rod 2 extends out through the guide module 12 and is subjected to the pressure of external deep-sea seawater. Therefore, the pressure difference can be flexibly controlled by controlling the cross-sectional ratio of the two ends of the rod 2. Based on this, the pressure difference generated between the two ends of the rod 2 can achieve the effect of pushing the rod 2 out, thereby realizing the power output of this solution.

[0056] In this embodiment, the rod 2 passes through the guide module 12 to output power outward. Therefore, the guide module 12 and the rod 2 not only need a dynamic seal to isolate the internal space from the external environment, but also need to further remove dirt adhering to the surface of the rod 2 during its extension and retraction to prevent it from obstructing the sliding position. For this purpose, a rod cleaning structure 121 is provided at the end of the guide module 12 away from the main cylinder 11. Thus, during the sliding process of the rod 2, the rod cleaning structure 121 can isolate the adhering dirt from the outside, ensuring the stable and reliable operation of this solution. In this embodiment, due to the high pressure of the deep-sea environment, the rod cleaning structure 121 is connected to the external deep-sea environment on both sides along the axial direction of the guide module 12. This ensures that the pressure around the rod cleaning structure 121 is consistent with the deep-sea environment, effectively avoiding structural deformation caused by external unilateral pressure, which is more beneficial to ensuring the cleaning performance of this solution.

[0057] In this embodiment, the switch control module 13 is used to control the connection between the inside of the cylinder unit 1 and the external deep-sea environment, so as to control the entry of external seawater to push the extension of the rod 2; wherein, the function of the switch control module 13 is to control the communication path between the rear end of the rod 2 and the rear chamber separated from the cylinder unit 1 and the outside, so as to realize the injection of external seawater, thereby applying force to the end of the rod 2.

[0058] like Figure 1As shown, according to one embodiment of the present invention, the end of the rod 2 extending outside the cylinder unit 1 is the working end, and the end of the rod 2 inside the cylinder unit 1 is the piston end; wherein, the end area of ​​the piston end is larger than the end area of ​​the working end; furthermore, when the switch control module 13 is turned on, the rod 2 achieves power output based on the different pressure differences at its two ends. In this embodiment, taking operation at a water depth of 4000m as an example, the inner diameter of the hollow part of the cylinder unit 1 is set to 50mm, and the diameter of the working end of the rod 2 is set to 30mm, then the thrust acting on the piston end of the rod 2 is 3.14 × 25 2 ×40=78500N, the thrust at the working end of rod 2 is 3.14 15 2 40 = 28260N, and the difference between the two is 50240N. At this point, the deep-sea power push rod outputs a thrust of 50240N, achieving a large thrust output. Similarly, the output thrust of the deep-sea power push rod designed according to this invention can be flexibly set according to the working water depth, the cross-sectional area of ​​cylinder unit 1 and rod body 2, and deep-sea power push rods with different thrust outputs can be obtained based on different usage requirements.

[0059] like Figure 2 As shown, according to one embodiment of the present invention, the rod cleaning structure 121 includes: a retaining ring structure 1211 and a flexible cleaning ring 1212 mounted on the retaining ring structure 1211; wherein, a first annular groove 1211a is provided on the inner side of the retaining ring structure 1211, the radially outer side of the flexible cleaning ring 1212 is embedded in the first annular groove 1211a, and the radially inner side of the flexible cleaning ring 1212 is in contact with the radially outer side of the rod 2; in this embodiment, the radially outer side of the flexible cleaning ring 1212 needs to be clamped or fixed by the retaining ring structure 1211 to prevent it from loosening during operation, thereby enabling the flexible cleaning ring 1212 to always perform cleaning operations in a fixed position during the extension and retraction of the rod 2, preventing it from being rotated into the gaps in front or behind. Furthermore, the retaining ring structure 1211 is provided with water-permeable channels 1211b for connecting the two axial sides of the retaining ring structure 1211, and the water-permeable channels 1211b are offset from the first annular groove 1211a along the radial direction of the retaining ring structure 1211. In this embodiment, multiple water-permeable channels 1211b can be arranged at intervals along the circumference of the retaining ring structure 1211, preferably at equal intervals. Of course, non-equal intervals can also be selected according to the actual shape of the retaining ring structure 1211, as long as the pressure can be kept consistent so that the flexible cleaning ring 1212 can maintain full communication with the external deep-sea environment on both sides.

[0060] Combination Figure 2 , Figure 3 and Figure 4As shown, according to one embodiment of the present invention, the retaining ring structure 1211 is an annular structure composed of multiple coaxial rings stacked sequentially. In this embodiment, the retaining ring structure 1211 is implemented using two coaxial rings, namely a first retaining ring portion 1211c and a second retaining ring portion 1211d. The first retaining ring portion 1211c and the second retaining ring portion 1211d can be pre-fixed to each other using locking connectors, or they can be fixed to each other when connected to the guide module 12. By adopting a split configuration, the processing of the retaining ring structure 1211 and the installation of the flexible cleaning ring 1212 can be facilitated. In this embodiment, a portion of the water-permeable channel 1211b is provided on both the first retaining ring portion 1211c and the second retaining ring portion 1211d. Therefore, during connection, they can be aligned with each other, which will not be elaborated further here. In this embodiment, the first annular groove 1211a for installing the flexible cleaning ring 1212 can be provided on the first retaining ring portion 1211c or the second retaining ring portion 1211d. The flexible cleaning ring 1212 can be fixed by the direct connection between the first retaining ring portion 1211c and the second retaining ring portion 1211d. Of course, in different embodiments, the retaining ring structure 1211 can also be set in three, four, or other ways, but it is necessary to ensure the connectivity of the permeable channel 1211b formed after its installation and the sealing of the connection position.

[0061] In another embodiment, the retaining ring structure 1211 can also be configured as an integral piece, which can be directly machined on the inner side to achieve the embedding and fixing of the flexible cleaning ring 1212.

[0062] like Figure 2 As shown, according to one embodiment of the present invention, the minimum radial dimension of the inner radial surface of the retaining ring structure 1211 is greater than the radial dimension of the corresponding position of the rod 2. In this embodiment, the smallest radial portion of the inner radial surface of the retaining ring structure 1211 is located at the rear end of the retaining ring structure 1211 to reduce the gap between the rear end of the retaining ring structure 1211 and the rod 2, thereby effectively blocking the flexible cleaning ring 1212 and preventing the bottom of the flexible cleaning ring 1212 from being rolled up.

[0063] Combination Figure 1 , Figure 2 and Figure 5As shown, according to one embodiment of the present invention, the flexible cleaning ring 1212 is configured to increase in size along the axial direction of the rod 2 on the side that contacts the rod 2, thereby effectively improving the corresponding cleaning range. Furthermore, an circumferential groove can be provided on the inner surface of the side of the flexible cleaning ring 1212 that contacts the rod 2, so that at least two annular cleaning portions 1212a are formed on the side of the flexible cleaning ring 1212 that contacts the rod 2. The multiple annular cleaning portions 1212a not only effectively ensure the cleaning range of the rod 2, but also effectively reduce the contact friction between them, thus being more beneficial to ensuring the effective power output of this solution.

[0064] According to one embodiment of the present invention, the annular cleaning portion 1212a formed on the flexible cleaning ring 1212 can be circular or conical. See also Figure 5 As shown, in this embodiment, the annular cleaning portion 1212a can be configured as a conical ring. Taking two annular cleaning portions 1212a as an example, the smaller diameter ends of the two annular cleaning portions 1212a are arranged in a direction that is far apart from each other. This allows the front annular cleaning portion 1212a to extend into the hollow portion of the first retaining ring portion 1211c, thereby making the cleaning range of the flexible cleaning ring 1212 on the rod 2 more extensive. Correspondingly, the annular grooves on the two annular cleaning portions 1212a can be configured as grooves with a trapezoidal or rectangular cross-section, depending on actual needs.

[0065] In this embodiment, the rear annular cleaning part 1212a and the rod body 2 are fitted with a clearance, or a through hole is provided on the rear annular cleaning part 1212a. This ensures that the pressure on the front annular cleaning part 1212a relative to both sides is balanced, further guaranteeing the operational stability and reliability of this solution.

[0066] In this embodiment, the angle between the front annular cleaning part 1212a and the rod 2 is 10° to 15°, and the axial length of the contact position between the annular cleaning part 1212a and the rod 2 is 2mm to 3mm. The annular cleaning part 1212a, as described above, effectively ensures the stability of cleaning the rod 2 while effectively suppressing and reducing friction between the annular cleaning part 1212a and the rod 2. Furthermore, the thickness of the annular cleaning part 1212a is 3mm to 4mm, thereby effectively ensuring the structural strength of the annular cleaning part 1212a, especially considering its inclined arrangement, which provides a more beneficial cleaning effect. Furthermore, the rear annular cleaning part 1212a has a thickness of 3mm to 4mm, an angle of 80° to 90° with the rod 2, and an axial length of 1mm to 2mm at the contact position with the rod 2. The above configuration effectively ensures the supporting role of the rear annular cleaning section 1212a on the overall flexible cleaning ring 1212, making the structure of the flexible cleaning ring 1212 more stable and reliable during the cleaning process.

[0067] Combination Figure 2 and Figure 5 As shown, according to one embodiment of the present invention, the rear end of the flexible cleaning ring 1212 may be further provided with an annular receiving groove 1212b with an opening facing the second retaining ring portion 1211d. Moreover, along the axial direction of the flexible cleaning ring 1212, there is an annular gap between the end of the annular cleaning portion 1212a at the rear end and the rear end face of the flexible cleaning ring 1212, and this annular gap is connected to the annular receiving groove 1212b. Thus, when installed in the first annular groove 1211a in the retaining ring structure 1211, the annular receiving groove 1212b can be connected to the gap between the retaining ring structure 1211 and the rod 3 based on the annular gap. Thus, the external high-pressure seawater through the water-permeable channel 1211b can directly fill the rear end of the flexible cleaning ring 1212 through the connected position, thereby achieving consistent pressure on the front and rear sides of the flexible cleaning ring 1212 and ensuring the reliable stability of the overall structure of the flexible cleaning ring 1212.

[0068] Combination Figure 2 , Figure 6 , Figure 7 , Figure 8As shown, according to one embodiment of the present invention, the guide module 12 further includes: a hollow guide cylinder 12a, a first sealing ring 122, a first retaining ring 123, and a guide sleeve 124 disposed within the guide cylinder 12a; wherein, along the direction from the front end to the rear end of the cylinder unit 1, the hollow portion of the guide cylinder 12a is sequentially provided with a first hollow portion, a second hollow portion, and a third hollow portion; in this embodiment, the radial dimensions of the first hollow portion, the second hollow portion, and the third hollow portion are different, thereby making the interior of the guide cylinder 12a a stepped hollow portion, with the radial dimension of the second hollow portion being the smallest, so as to allow the rod 2 to pass through smoothly, while the first sealing ring 122 and the first retaining ring 123 are disposed in the first hollow portion, and the first retaining ring 123 abuts against the first sealing ring 122 and the guide cylinder 12a on both axial sides respectively; in this embodiment, the position of the guide cylinder 12a abutting against the first retaining ring 123 is the stepped surface formed by the radial difference between the first hollow portion and the second hollow portion. In this embodiment, the guide sleeve 124 is installed in the third hollow part by means of an interference fit.

[0069] In this embodiment, the radial dimension of the second hollow portion is greater than the radial dimension of the portion through which the rod 2 passes, and the radial dimension of the first retaining ring 123 is also greater than the radial dimension of the portion through which the rod 2 passes. This effectively avoids contact with the surface of the rod 2. As a result, the distance between the first sealing ring 122 and the bearing position of the guide cylinder 12a can be effectively increased by the spacing effect of the first retaining ring 123. This effectively prevents the first sealing ring 122 from being rolled into the gap between the second hollow portion and the rod 2 during the retraction of the rod 2, which is more beneficial to ensuring the structural integrity and service life of the first sealing ring 122.

[0070] In this embodiment, the first sealing ring 122 is a U-shaped sealing ring, and the opening direction of the first sealing ring 122 is opposite to that of the first retaining ring 123. In this embodiment, the two annular sidewalls on the opening side of the first sealing ring 122 extend in a direction away from each other, thereby enabling the opening side of the first sealing ring 122 to more reliably contact the first hollow part and the rod body 2, so as to achieve a reliable sealing effect.

[0071] In this embodiment, the first sealing ring 122 is made of fluororubber, which effectively ensures the stability and reliability of its structure, enabling this solution to fully meet the performance requirements under the high pressure environment of the deep sea.

[0072] In this embodiment, the first retaining ring 123 is made of polytetrafluoroethylene. Due to its higher hardness compared to the first sealing ring 122, it can effectively limit the first sealing ring 122. Furthermore, due to the relatively lower friction of the first retaining ring 123, the gap between it and the rod 2 can be further reduced, making the blocking effect on the first sealing ring 122 more sufficient and effectively ensuring the structural safety of the first sealing ring 122 during operation.

[0073] like Figure 2 As shown, according to one embodiment of the present invention, the retaining ring structure 1211 can be fixed to the front end of the guide cylinder 12a based on the locking connector. Furthermore, the rear end of the retaining ring structure 1211 can be partially coaxially sleeved with the front end of the guide cylinder 12a. This ensures sufficient coaxial accuracy during installation and makes the installation of the retaining ring structure 1211 more stable. In addition, based on this mutually sleeved positioning installation method, there is a certain gap between the rear end of the retaining ring structure 1211 and the front end of the first sealing ring 122. This allows the first sealing ring 122 to be effectively sealed inside while also providing a certain sliding space, preventing compression deformation of the first sealing ring 122. Moreover, even if the first sealing ring 122 is rolled into the gap between the rod 2 and other structures, it can be pushed out during the reverse movement of the rod 2 based on its certain sliding space. This makes the solution have a certain self-correcting ability for possible roll-in defects of the first sealing ring 122 during operation, which is more beneficial to improving the operational reliability of the solution in special environments.

[0074] Combination Figure 1 and Figure 2 As shown, according to one embodiment of the present invention, the guide cylinder 12a is connected to the end of the main cylinder 11 by an insert-nesting method. An O-ring is provided between the guide cylinder 12a and the main cylinder 11 to ensure the sealing between the connection points. Furthermore, an annular clearance groove can be further machined on the outer surface of the portion of the guide cylinder 12a inserted into the main cylinder 11, and this annular clearance groove is located behind the O-ring to avoid the influence of machining errors on the outer surface of the excessively long insertion portion on the installation sealing performance.

[0075] Furthermore, a radially protruding annular boss can be further provided on the outer surface of the guide cylinder 12a. Since the annular boss abuts against the end of the main cylinder 11, the installation position of the guide cylinder 12a is restricted, and it is convenient to lock the connector to fix it to the main cylinder 11. In this embodiment, an O-ring can be further provided between the annular boss and the end of the main cylinder 11 to further improve the sealing performance between the connection points.

[0076] Combination Figure 1and Figure 2 As shown, according to one embodiment of the present invention, the guide sleeve 124 is nested and inserted into the rear end of the guide cylinder 12a, and the interference fit between the guide sleeve 124 and the guide cylinder 12a is set at 0.02mm~0.04mm to ensure the reliability and stability of its installation. In this embodiment, the guide sleeve 124 can be configured as a cylinder, and through holes are regularly arranged on its side wall. Graphite is added to the through holes to reduce frictional resistance, thereby reducing friction and improving its wear resistance. In this embodiment, a radially protruding guide sleeve limiting part can be further provided at the rear end of the guide sleeve 124 to achieve accurate positioning with the guide cylinder 12a.

[0077] Combination Figure 1 and Figure 9 As shown, according to one embodiment of the present invention, a piston structure 21 is provided at the piston end of the rod 2; wherein, a second annular groove 21a is provided on the outer side of the piston structure 21, and a second sealing ring 21b and a second retaining ring 21c are sleeved in the second annular groove 21a; in this embodiment, the opposite sides of the second retaining ring 21c abut against the second sealing ring 21b and the piston structure 21, respectively. In this embodiment, the radial dimension of the outer side of the piston structure 21 is consistent with the radial dimension of the inner side of the main cylinder 11, so as to ensure its sliding effect along the main cylinder 11. Moreover, the second sealing ring 21b further ensures the sealing between them, so as to avoid leakage of seawater injected from the rear to the front, which is more beneficial to ensuring the efficiency of power output.

[0078] In this embodiment, the second sealing ring 21b is a U-shaped sealing ring, and the opening direction of the second sealing ring 21b is opposite to that of the second retaining ring 21c. In this embodiment, the two annular sidewalls on the opening side of the second sealing ring 21b extend in a direction away from each other, thereby enabling the opening side of the second sealing ring 21b to more reliably contact the main cylinder 11 and the piston structure 21 to achieve a reliable sealing effect.

[0079] In this embodiment, the second sealing ring 21b is made of fluororubber, which effectively ensures the stability and reliability of its structure, enabling this solution to fully meet the performance requirements under the high pressure environment of the deep sea.

[0080] In this embodiment, the second retaining ring 21c is disposed between the piston structure 21 and the second sealing ring 21b, so that the second sealing ring 21b is away from the position where the piston structure 21 directly contacts the main cylinder 11. This effectively prevents the second sealing ring 21b from being directly rolled into the space between the piston structure 21 and the main cylinder 11, ensuring the working stability of the second sealing ring 21b. Furthermore, the second retaining ring 21c is made of polytetrafluoroethylene (PTFE). Due to its higher hardness compared to the second sealing ring 21b, it can effectively limit the second sealing ring 21b. Moreover, due to the relatively lower friction of the second retaining ring 21c, the gap between it and the main cylinder 11 can be further reduced, making the blocking effect on the second sealing ring 21b more sufficient and effectively ensuring the structural safety of the second sealing ring 21b during operation.

[0081] Combination Figure 1 and Figure 9 As shown, according to one embodiment of the present invention, the piston structure 21 and the rod 2 are detachably connected. Specifically, the piston structure 21 can be configured as a ring structure, which can then be directly fitted onto the end of the rod 2 and positioned based on the ring-shaped limiting boss on the rod 2. Preferably, a locking connection using a nut and spring washer is used to secure it. In this embodiment, to ensure sealing between the connection points, O-rings can be further provided at the designated positions of the piston structure 21 and the rod 2 to effectively prevent seawater leakage.

[0082] Combination Figure 1 and Figure 9 As shown, according to one embodiment of the present invention, the piston structure 21 can be configured as a split structure, comprising a piston structure body and a piston baffle. This allows the second annular groove 21a to be disposed at the end of the piston structure body, facilitating the installation of the second sealing ring 21b and the second retaining ring 21c. Furthermore, the relative fixation of the piston structure body and the piston baffle enables the restriction of the second sealing ring 21b and the second retaining ring 21c. In this embodiment, along the axial direction of the rod 2, the width of the second annular groove 21a is greater than the width of the combined structure of the second sealing ring 21b and the second retaining ring 21c. This provides the second sealing ring 21b with a certain sliding space, preventing it from being compressed and deformed. Moreover, even if the second sealing ring 21b is caught in the gap between other structures, its sliding space allows the caught portion to be pushed out during the reverse movement of the rod 2. This provides the solution with a certain self-correcting capability against potential catching defects of the second sealing ring 21b during operation, which is beneficial for improving the operational reliability of the solution under special environments.

[0083] Combination Figure 1 and Figure 9As shown, according to one embodiment of the present invention, an anti-wear ring 21d is nested on the outer side of the piston structure 21. In this embodiment, the anti-wear ring 21d is made of phenolic resin reinforced with cotton fabric; wherein, the anti-wear ring 21d and the piston structure 21 can be fixed by means of gluing or other methods, so that the sliding friction during the movement can be effectively reduced based on the sliding contact between the anti-wear ring 21d and the main cylinder 11, thereby avoiding scratches caused by direct contact between the piston structure 21 and the main cylinder 11, effectively ensuring the sealing of the sliding position, and improving the service life of this solution.

[0084] In this embodiment, the piston structure 21 is preferably installed inside the main cylinder 11 with a clearance fit, thereby effectively avoiding direct contact between the piston structure 21 and the main cylinder 11; wherein, the clearance between the piston structure 21 and the main cylinder 11 is designed to be 0.1mm-0.2mm, so as to ensure the sealing performance of this solution while avoiding direct contact.

[0085] In this embodiment, the anti-wear ring 21d covers more than 60% of the outer ring surface of the piston structure 21 to ensure sufficient sliding contact area between the piston structure 21 and the main cylinder 11, thereby ensuring posture stability during sliding. Furthermore, to reduce friction during sliding, the surface roughness of the outer ring surface of the anti-wear ring 21d should be better than Ra3.2.

[0086] like Figure 1 and Figure 10 As shown, according to one embodiment of the present invention, the switch control module 13 includes: an end cap 131, a throttle valve 132, and a control switch 133; in this embodiment, the end cap 131 has an input channel extending through its opposite sides at its center; furthermore, the throttle valve 132 and the control switch 133 are installed at opposite ends of the input channel, wherein the throttle valve 132 is arranged inside the cylinder unit 1, and the speed at which fluid enters the cylinder unit 1 can be adjusted by the size of the opening at the center of the throttle valve 132, thereby adjusting the movement speed of the rod 2.

[0087] In this embodiment, the surface roughness of the inner side of the central opening of the throttle valve 132 should be better than Ra3.2, and the consistency should be kept within ±Ra0.5, so as to keep the throttling effect on the liquid stable.

[0088] like Figure 1 As shown, according to one embodiment of the present invention, the control switch 133 is one of a solenoid valve switch and a pressure rupture disc.

[0089] like Figure 1As shown, according to one embodiment of the present invention, the end cap 131 is installed by partially extending into the main cylinder 11, while the remaining portion of the end cap 131 abuts against the end of the main cylinder 11. O-rings are provided at both the abutment position of the end cap 131 and the nesting position of the end cap 131 with the main cylinder 11 to improve the sealing performance of the connection. Furthermore, the abutment position of the end cap 131 with the main cylinder 11 is further secured with a locking connector to ensure reliable installation.

[0090] To further illustrate this scheme, its initial state is described.

[0091] Specifically, during the initial assembly of the deep-sea power push rod, the space between the piston end of the rod body 2 and the switch control module 13 is filled with oil, and the piston structure 21 is located at the front end of the cylinder unit 1 (i.e., Figure 1 (Leftmost in the diagram) When the deep-sea power push rod reciprocates, the rod 2 moves to the right. At this time, the guide module 12 and the front end of the piston structure 21 are in a vacuum state, with only a back pressure of 1 atmosphere (i.e., 0.1 MPa). During deep-sea operation, this 0.1 MPa back pressure will not affect the operation of the entire deep-sea power push rod. When on the sea surface, due to the load on the rod 2, the force generated by the 0.1 MPa back pressure is small and will not affect the system. Therefore, during deep-sea operation, after first draining the internal oil from the initial assembly, the external seawater is allowed to enter by controlling the connection through the switch control module 13, thus achieving the corresponding power output effect.

[0092] The above description is merely an example of a specific solution of the present invention. For any devices and structures not described in detail herein, it should be understood that they are implemented using common devices and methods already available in the art.

[0093] The above description is merely one embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the invention by those skilled in the art. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A deep-sea powered actuator, characterized in that, include: Cylinder block unit (1), rod body (2); The rod (2) and the cylinder unit (1) are slidably connected by a dynamic seal. The cylinder unit (1) includes: a main cylinder (11) with openings at both ends, a guide module (12) sealed to the front end of the main cylinder (11), and a switch control module (13) sealed to the rear end of the main cylinder (11). The guide module (12) is provided with a rod cleaning structure (121) at the end away from the main cylinder (11); Along the axial direction of the guide module (12), the rod cleaning structure (121) is in communication with the external deep-sea environment on opposite sides; The switch control module (13) is used to control the connection between the inside of the cylinder unit (1) and the external deep-sea environment, so as to control the entry of external seawater to push the rod (2) to extend. The rod cleaning structure (121) includes: a retaining ring structure (1211) and a flexible cleaning ring (1212) installed on the retaining ring structure (1211). The inner side of the retaining ring structure (1211) is provided with a first annular groove (1211a), the outer radial side of the flexible cleaning ring (1212) is embedded in the first annular groove (1211a), and the inner radial side of the flexible cleaning ring (1212) is in contact with the outer radial side of the rod (2). The retaining ring structure (1211) is provided with a first retaining ring portion (1211c). The flexible cleaning ring (1212) is provided with an circumferential groove on the side that contacts the rod (2) so that at least two annular cleaning portions (1212a) are formed on the side that contacts the rod (2); wherein, the annular cleaning portions (1212a) are provided in a conical shape. The annular cleaning section (1212a) at the front extends into the hollow part of the first retaining ring section (1211c); The rear annular cleaning part (1212a) and the rod (2) are fitted with a clearance, or a through hole is provided on the rear annular cleaning part (1212a); The angle between the front annular cleaning part (1212a) and the rod (2) is 10° to 15°, and the angle between the rear annular cleaning part (1212a) and the rod (2) is 80° to 90°. The flexible cleaning ring (1212) has an annular receiving groove (1212b) at its rear end, and along the axial direction of the flexible cleaning ring (1212), there is a gap between the end of the rear annular cleaning part (1212a) and the rear end face of the flexible cleaning ring (1212).

2. The deep-sea power push rod according to claim 1, characterized in that, The end of the rod (2) that extends outside the cylinder unit (1) is the working end, and the end of the rod (2) that is inside the cylinder unit (1) is the piston end; The end area of ​​the piston end is greater than the end area of ​​the working end; When the switch control module (13) is turned on, the rod (2) outputs power based on the different pressure differences at both ends.

3. The deep-sea power push rod according to claim 1 or 2, characterized in that, The retaining ring structure (1211) is provided with a water-permeable channel (1211b) for connecting the two axial sides of the retaining ring structure (1211), and the water-permeable channel (1211b) is offset from the first annular groove (1211a) along the radial direction of the retaining ring structure (1211).

4. The deep-sea power push rod according to claim 3, characterized in that, The retaining ring structure (1211) is an integral ring structure, or the retaining ring structure (1211) is a ring structure composed of multiple coaxial ring bodies stacked in sequence.

5. The deep-sea power push rod according to claim 3, characterized in that, The minimum radial dimension of the inner radial side of the retaining ring structure (1211) is greater than the radial dimension of the corresponding position of the rod (2).

6. The deep-sea power push rod according to claim 1 or 2, characterized in that, The guide module (12) further includes: a hollow guide cylinder (12a), a first sealing ring (122), a first retaining ring (123), and a guide sleeve (124) disposed inside the guide cylinder (12a). Along the direction from the front end to the rear end of the cylinder unit (1), the hollow part of the guide cylinder (12a) is provided with a first hollow part, a second hollow part and a third hollow part in sequence; The first sealing ring (122) and the first retaining ring (123) are disposed in the first hollow part, and the first retaining ring (123) abuts against the first sealing ring (122) and the guide cylinder (12a) on both axial sides respectively; The guide sleeve (124) is installed in the third hollow part by means of an interference fit.

7. The deep-sea power push rod according to claim 6, characterized in that, The piston end of the rod (2) is provided with a piston structure (21). The piston structure (21) is provided with a second annular groove (21a) on the outside, and a second sealing ring (21b) and a second retaining ring (21c) are sleeved in the second annular groove (21a). The two opposite sides of the second retaining ring (21c) abut against the second sealing ring (21b) and the piston structure (21), respectively.

8. The deep-sea power push rod according to claim 7, characterized in that, The outer surface of the piston structure (21) is nested with an anti-wear ring (21d).

9. The deep-sea power push rod according to claim 8, characterized in that, Both the first sealing ring (122) and the second sealing ring (21b) are U-shaped sealing rings, and the material used is fluororubber; The first retaining ring (123) and the second retaining ring (21c) are made of polytetrafluoroethylene; The anti-wear ring (21d) is made of phenolic resin reinforced with cotton fabric.

10. The deep-sea power push rod according to claim 1 or 2, characterized in that, The switch control module (13) includes: an end cap (131), a throttle valve (132), and a control switch (133). The end cap (131) has an input channel running through its opposite sides at its center; The throttle valve (132) and the control switch (133) are installed at opposite ends of the input channel, wherein the throttle valve (132) is arranged inside the cylinder block unit (1); The control switch (133) is one of a solenoid valve switch or a pressure rupture disc.

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