Efficient automatic cleaning equipment for cargo oil tank of oil tanker

Abstract

The present application relates to the technical fields of marine engineering equipment and ship equipment, in particular to a high-efficiency automatic cleaning equipment for cargo oil tank of oil tanker, comprising a liquid supply pipe, a nozzle assembly and a shell, the nozzle assembly is rotatably arranged on the shell; a rotatable rotating part is arranged in the shell, an impeller is fixedly arranged in the rotating part, and a pressure relief channel, an adjusting mechanism and a reset assembly are arranged on the rotating part, the displacement of the adjusting mechanism can control the opening and closing of the pressure relief channel; through the cooperation of the adjusting mechanism and the reset assembly, the high-pressure constant-speed characteristic is realized, so that the nozzle can still maintain a relatively low constant speed under extremely high injection pressure. This greatly increases the residence time of high-energy jet flow on stubborn dirt surface, realizes the double maximization of striking force and cleaning time, and significantly improves the cleaning cleanliness.

Description

Technical Field

[0001] This invention relates to the field of marine engineering equipment and ship equipment technology, specifically to a high-efficiency automatic tank cleaning device for oil tanker cargo oil tanks. Background Technology

[0002] Oil tankers, as a type of marine engineering transport vessel, are crucial marine engineering transportation equipment. After unloading, the deep bulkheads and complex hull structure of their cargo oil tanks often retain large amounts of crude oil, wax, and deep-seated sludge. Since cargo oil tanks are flammable and explosive enclosed marine engineering operation spaces, a thorough cleaning of the ship's interior is essential to ensure navigational safety and compliance with marine environmental regulations.

[0003] Among existing marine tank cleaning equipment, fully hydraulically driven tank cleaning machines, which utilize fluid pressure as a power source, are widely used as core marine engineering cleaning equipment because they completely eliminate electrical components and highly meet the stringent explosion-proof safety standards of marine cargo oil tanks. For example, Chinese Patent Publication No. CN101948003B discloses a fully automatic tank cleaning machine, which includes an upper water inlet seat, a main water pipe, a lower water inlet seat, and nozzles; a rotating mechanism is arranged in the upper water inlet seat, and an oscillating mechanism is arranged in the lower water inlet seat. The water flow entering through the inlet drives the rotating mechanism in the upper water inlet seat to rotate, thereby driving the lower water inlet seat to rotate as a whole through the main water pipe; at the same time, the water flow enters the lower water inlet seat through the main water pipe, driving the oscillating mechanism to move the nozzles to oscillate and spray water. The advantage of this technical solution is that the only power source is pressurized water, the entire operation is completed mechanically, the structure is safe, and it is particularly suitable for cleaning in flammable and explosive environments such as oil tankers. Because its drive mechanism (such as a rotating mechanism or impeller) is directly driven by the fluid flow rate and velocity, according to the fluid mechanical characteristics, the higher the pressure of the input fluid and the faster the flow rate, the faster the rotation speed of the drive mechanism. This leads to an irreconcilable cleaning contradiction: cleaning failure under high pressure conditions. When facing stubborn old sludge or hard wax layers adhering to complex components such as the hull wall and reinforcing ribs of a ship, operators often need to increase the supply pressure to obtain a greater jet impact force. However, for the existing equipment mentioned above, the increase in pressure will cause the nozzle rotation or oscillation speed to increase sharply. The excessively fast scanning speed results in insufficient residence time of the high-energy jet on the surface of the dirt. The jet often passes by quickly and cannot complete deep peeling and breaking, resulting in the phenomenon that the water pressure is high but the dirt is not cleaned. Conversely, if the rotation speed is reduced to ensure sufficient residence time, the supply pressure must be reduced, which directly leads to insufficient jet impact force and also fails to remove stubborn dirt. Summary of the Invention

[0004] To address the aforementioned issues, a high-efficiency automatic tank cleaning device for oil tanker cargo tanks is provided. By incorporating an adjustment mechanism and a reset component, it achieves high-pressure constant-speed characteristics, ensuring that the nozzle maintains a low, constant rotational speed even under extremely high jet pressure. This significantly increases the residence time of the high-energy jet on stubborn dirt surfaces, maximizing both impact force and cleaning time, and significantly improving cleaning effectiveness.

[0005] To address the problems of existing technologies, this invention provides a high-efficiency automatic tank cleaning device for oil tanker cargo tanks, including a liquid supply pipe and a nozzle assembly, and a housing fitted around the outer periphery of the liquid supply pipe. The nozzle assembly is rotatably mounted on the housing. A rotatable rotating component is disposed within the housing and fitted around the outer periphery of the liquid supply pipe. An impeller, subjected to fluid impact and rotation, is fixedly disposed within the rotating component, and a pressure relief channel is provided on the rotating component. The pressure relief channel is configured to draw fluid out without passing through the impeller. The nozzle assembly is drivenly connected to the rotating component. The rotating component also contains a pressure relief channel. The fluid pressure in the supply pipe drives a sliding adjustment mechanism that can reciprocate along the axis of the rotating component and a reset assembly that provides a reverse biasing force against the adjustment mechanism. The displacement of the adjustment mechanism can control the opening and closing of the pressure relief channel. The adjustment mechanism is configured to keep the pressure relief channel closed when the fluid pressure is below a preset threshold, so that the rotational speed of the nozzle assembly increases with the increase of pressure. When the fluid pressure exceeds the preset threshold, the sliding adjustment mechanism overcomes the biasing force of the reset assembly to open the pressure relief channel, so as to divert the fluid and keep the rotational speed of the nozzle assembly within a preset constant range.

[0006] Preferably, the regulating mechanism includes a valve core with a flow channel. When the fluid pressure is lower than a preset threshold, the solid part of the valve core blocks the pressure relief channel. When the fluid pressure exceeds the preset threshold, the valve core is displaced, causing the flow channel to connect the pressure relief channel with the fluid environment in the supply pipe, thereby implementing flow diversion.

[0007] Preferably, the rotating component is provided with a hydraulic feedback assembly; the hydraulic feedback assembly includes a connecting channel opened in the rotating component and a hydraulic medium filled in the connecting channel, as well as push rods with sliding seals at both ends of the connecting channel; one end of the two push rods acts on the hydraulic medium, and the other end abuts against different axial positions on the outer wall of the valve core, forming a hydraulic closed-loop linkage structure.

[0008] Preferably, the outer wall of the valve core is provided with at least two guide cone surfaces; the guide cone surfaces cooperate with the abutting ends of the two push rods; when the valve core moves axially, the slope of the guide cone surfaces drives one of the push rods to retract into the connecting flow channel, while the hydraulic medium drives the other push rod to extend out of the connecting flow channel.

[0009] Preferably, the connecting flow channel is constructed as a damping channel; when the valve core is displaced by the impact of fluid pressure, the hydraulic medium is forced to flow in the connecting flow channel and generate viscous damping force, which is used to suppress the high-frequency oscillation of the valve core and maintain the dynamic stability of the adjustment process.

[0010] Preferably, a plurality of arrayed throttling orifices are provided on one end of the flow channel near the liquid supply pipe; the throttling orifices are used to form a multi-stage pressure drop in the initial stage of opening the pressure relief channel, smoothing the sudden change in flow rate during the pressure relief process.

[0011] Preferably, the reset component is one or a combination of a helical spring, a disc spring, a wave spring, or a pneumatic spring; the reset component is coaxially sleeved on the outer periphery of the adjusting mechanism or abuts against the end of the adjusting mechanism.

[0012] Preferably, the outlet of the pressure relief channel is connected to the water outlet area downstream of the impeller to discharge the diverted fluid.

[0013] Preferably, the inner wall of the rotating component is provided with an annular limiting step to limit the maximum axial displacement limit of the adjusting mechanism in the adjusted state, so as to prevent the adjusting mechanism from disengaging from or excessively compressing the reset component.

[0014] Preferably, a gear reducer is further provided between the nozzle assembly and the rotating component.

[0015] The advantages of this invention compared to the prior art are: 1. This invention, through the coordination of an adjustment mechanism and a reset component, creates two distinct operating modes within the machine. Under low pressure, the pressure relief channel is closed, and the equipment maintains a characteristic of increasing rotation speed with increasing pressure, suitable for rapid scanning and wetting. Once the pressure exceeds a threshold and enters the high-pressure zone, the adjustment mechanism will axially displace under fluid pressure to open the pressure relief channel for diversion, locking the flow through the impeller. This achieves a high-pressure constant-speed characteristic, allowing the nozzle to maintain a relatively low constant rotation speed even under extremely high jet pressure. This significantly increases the residence time of the high-energy jet on the surface of stubborn dirt, maximizing both impact force and cleaning time, and significantly improving cleaning cleanliness.

[0016] 2. This invention achieves control by sealing the valve core and connecting the flow channel. Compared to traditional lift valves, the shear-type opening and closing mechanism of the slide valve structure provides better linear response to fluid pressure and enables more precise control of the flow distribution ratio. Furthermore, this structure is less prone to particle jamming in marine cargo oil cleaning environments containing high-viscosity oil sludge and waxy particles, ensuring the long-term reliable operation of the marine tank cleaning equipment under complex and harsh marine conditions and contributing to the stability of constant speed control. Attached Figure Description

[0017] Figure 1 A three-dimensional structural diagram of a high-efficiency automatic tank cleaning device for oil tankers. Figure 1 .

[0018] Figure 2 A three-dimensional structural diagram of a high-efficiency automatic tank cleaning device for oil tankers. Figure 2 .

[0019] Figure 3 This is a schematic cross-sectional view of the depressurization channel in a high-efficiency automatic tank cleaning device for oil tankers when it is open.

[0020] Figure 4 yes Figure 3 Enlarged view of point A in the middle.

[0021] Figure 5 This is a three-dimensional cross-sectional diagram of the depressurization channel in a high-efficiency automatic tank cleaning device for oil tankers when it is open.

[0022] Figure 6 yes Figure 5 Enlarged view of point B in the middle.

[0023] Figure 7 This is a schematic cross-sectional view of the depressurization channel in a high-efficiency automatic tank cleaning system for oil tankers when it is closed.

[0024] Figure 8 This is a three-dimensional cross-sectional diagram of the depressurization channel in a high-efficiency automatic tank cleaning device for oil tankers when it is closed.

[0025] Figure 9 This is a three-dimensional structural diagram of rotating components and a gear reducer in a high-efficiency automatic tank cleaning system for oil tankers. Figure 1 .

[0026] Figure 10 This is a three-dimensional structural diagram of rotating components and a gear reducer in a high-efficiency automatic tank cleaning system for oil tankers. Figure 2 .

[0027] Figure 11 This is a three-dimensional structural diagram of the valve core in a high-efficiency automatic tank cleaning device for oil tankers.

[0028] The following components are labeled in the diagram: 1. Liquid supply pipe; 2. Housing; 21. Nozzle assembly; 211. Gear reducer; 22. Rotating component; 221. Impeller; 222. Pressure relief channel; 223. Adjustment mechanism; 2231. Valve core; 22311. Guide cone surface; 22312. Throttling orifice; 2232. Flow channel; 224. Reset assembly; 225. Hydraulic feedback assembly; 2251. Connecting flow channel; 2252. Push rod; 226. Limiting step. Detailed Implementation

[0029] To further understand the features, technical means, and specific objectives and functions achieved by the present invention, the present invention will be described in further detail below with reference to the accompanying drawings and specific embodiments.

[0030] like Figures 1 to 9 The diagram shows a high-efficiency automatic tank cleaning device for oil tanker cargo tanks, comprising a liquid supply pipe 1 and a nozzle assembly 21, and a housing 2 sleeved around the outer periphery of the liquid supply pipe 1. The nozzle assembly 21 is rotatably mounted on the housing 2. A rotatable rotating component 22 is disposed inside the housing 2 and is sleeved around the outer periphery of the liquid supply pipe 1. An impeller 221, which rotates under the impact of fluid, is fixedly disposed inside the rotating component 22, and a pressure relief channel 222 is provided on the rotating component 22. The pressure relief channel 222 is configured to draw out the fluid without passing through the impeller 221. The nozzle assembly 21 is kinetically connected to the rotating component 22. The rotating component 22 is also provided with a nozzle for receiving the fluid from the liquid supply pipe 1. The body pressure drives the reciprocating sliding adjustment mechanism 223 along the axial direction of the rotating member 22 and the reset assembly 224 for providing a reverse biasing force against the adjustment mechanism 223. The displacement of the adjustment mechanism 223 can control the opening and closing of the pressure relief channel 222. The adjustment mechanism 223 is configured to keep the pressure relief channel 222 closed when the fluid pressure is lower than a preset threshold, so that the rotational speed of the nozzle assembly 21 increases with the increase of pressure. When the fluid pressure exceeds the preset threshold, the adjustment mechanism 223 is slid open to open the pressure relief channel 222 against the biasing force of the reset assembly 224, so as to divert the fluid and keep the rotational speed of the nozzle assembly 21 within a preset constant range.

[0031] In existing tanker cargo oil tank cleaning operations, traditional hydraulically driven tank cleaning machines typically clean oil tanks by leveraging the linear coupling characteristic of higher pressure and faster rotation speed. While high pressure provides greater impact force, excessively high rotation speeds drastically shorten the residence time of the water jet on the dirt surface, resulting in ineffective cleaning.

[0032] To resolve this contradiction, this embodiment constructs a tank cleaning device with dual-mode operation capability. Its core lies in the pressure-speed decoupling mechanism integrated within the rotating component 22. First, high-pressure cleaning fluid enters from the supply pipe 1, impacting the impeller 221 within the rotating component 22. The rotation of the impeller 221, through a transmission connection, drives the nozzle assembly 21 mounted on the housing 2 to rotate, performing omnidirectional scanning cleaning. When the fluid pressure in the supply pipe 1 is at a low level, i.e., below a preset threshold, the reverse bias force (such as the spring force) provided by the reset component 224 is greater than the thrust generated by the fluid pressure on the regulating mechanism 223. At this time, the regulating mechanism 223 is firmly held in its initial position, completely locking and sealing the pressure relief channel 222 on the rotating component 22. All fluid entering the supply pipe 1 must pass through the impeller 221 to perform work. Therefore, in this stage, as the pressure increases, the system flow rate increases, and the impeller 221 speed increases linearly in a positive correlation, suitable for rapid initial wetting and ash rinsing of the tank walls.

[0033] When the fluid pressure continues to rise and exceeds a preset threshold, the thrust generated by the fluid on the force-bearing surface of the regulating mechanism 223 overcomes the biasing force of the reset assembly 224, pushing the regulating mechanism 223 to slide along the axis of the rotating component 22. This displacement directly opens the pressure relief channel 222, allowing a portion of the high-pressure fluid to be diverted directly without passing through the impeller 221. Furthermore, the higher the supply pressure, the greater the axial displacement of the regulating mechanism 223, the larger the opening of the pressure relief channel 222, and the higher the diversion ratio. This results in the effective flow rate through the impeller 221 being peaked and valleyed, thereby locking the rotational speed of the impeller 221 within a preset constant range.

[0034] The above method completely breaks the defect of pressure and speed lock in traditional tank cleaning machines, and achieves both great jet impact force and low and constant speed of nozzle assembly 21 under high pressure conditions, ensuring that the high-energy water jet has enough time to peel off stubborn oil sludge, significantly improving cleaning efficiency and deep cleanliness.

[0035] like Figures 3 to 8 and Figure 11 As shown: The regulating mechanism 223 includes a valve core 2231, on which a flow channel 2232 is provided; when the fluid pressure is lower than a preset threshold, the solid part of the valve core 2231 blocks the pressure relief channel 222; when the fluid pressure exceeds the preset threshold, the valve core 2231 is displaced, so that the flow channel 2232 connects the pressure relief channel 222 with the fluid environment in the liquid supply pipe 1, thereby implementing flow diversion.

[0036] During pressure regulation, the execution accuracy and sealing reliability of the regulating mechanism 223 directly determine the stability of the system. In this embodiment, the regulating mechanism 223 adopts a slide valve structure. The valve core 2231 serves as its actuating element, and a specific flow channel 2232 is pre-fabricated inside. In the initial state where the pressure is below the threshold, the solid wall surface of the valve core 2231, i.e., the non-porous area, faces the inlet of the pressure relief channel 222 on the rotating component 22, achieving a hard seal through high-precision fit, ensuring low-pressure full-flow drive. When the fluid pressure exceeds the preset threshold, pushing the valve core 2231 to produce axial displacement, the flow channel 2232 on the valve core 2231 gradually coincides with or aligns with the pressure relief channel 222 on the rotating component 22. The axial displacement of the valve core 2231 on the rotating component 22 determines the overlapping area of ​​the flow channel 2232 and the pressure relief channel 222, thereby achieving linear and precise control of the diverted flow rate. Utilizing the shear-type opening and closing characteristics of the slide valve structure, it offers stronger resistance to lateral fluid disturbances and more precise opening control compared to lift valves. The design of the solid seal and the 2232 flow channel simplifies the sealing logic, providing better resistance to dirt and jamming in cargo oil cleaning environments containing oil particles, thus extending the equipment's maintenance-free cycle.

[0037] like Figures 3 to 8 and Figure 11 As shown: The rotating component 22 is provided with a hydraulic feedback assembly 225; the hydraulic feedback assembly 225 includes a connecting channel 2251 opened in the rotating component 22 and a hydraulic medium filled in the connecting channel 2251, and push rods 2252 that are slidably sealed at both ends of the connecting channel 2251; one end of the two push rods 2252 acts on the hydraulic medium, and the other end abuts against different axial positions on the outer wall of the valve core 2231, forming a hydraulic closed-loop linkage structure.

[0038] In environments with high-speed rotation and intense fluid pulsation, the valve core 2231 is prone to high-frequency chatter, leading to unstable water output and even fatigue damage to components. Therefore, this embodiment incorporates an independent hydraulic feedback assembly 225 within the rotating component 22. A connecting flow channel 2251 is formed within the wall thickness of the rotating component 22, and push rods 2252 are installed at both ends of the connecting flow channel 2251, filled with incompressible hydraulic medium (such as hydraulic oil). The inner ends of the two push rods 2252 are in contact with the hydraulic medium, while their outer ends abut against different axial positions on the outer wall of the valve core 2231. This forms a hydraulic closed-loop linkage structure; any axial movement of the valve core 2231 must be accompanied by the flow of the internal hydraulic medium, i.e., the retraction or extension of the two push rods 2252. By utilizing the incompressibility and transmissibility of the liquid, the movement of the valve core 2231 is forcibly coupled with the internal hydraulic circuit, increasing the rigidity of the motion system.

[0039] like Figures 3 to 8 and Figure 11 As shown: The outer wall of the valve core 2231 is provided with at least two guide cone surfaces 22311; the guide cone surfaces 22311 cooperate with the abutting ends of the two push rods 2252; when the valve core 2231 moves axially, the slope of the guide cone surfaces 22311 drives one of the push rods 2252 to retract into the connecting flow channel 2251, while the other push rod 2252 is driven to extend outward from the connecting flow channel 2251 through the transmission of the hydraulic medium.

[0040] At least two guide cone surfaces 22311 with opposite directions or specific angles are machined on the outer wall of the valve core 2231. When the valve core 2231 is pressed and slides axially along the rotating component 22, one of the guide cone surfaces 22311 acts like a wedge, pressing the corresponding push rod 2252 and forcing it into the connecting flow channel 2251. The pressed-in push rod 2252 causes the oil pressure in the connecting flow channel 2251 to increase. Under the action of Pascal's principle, the hydraulic medium is transmitted to the other end of the connecting flow channel 2251, pushing up the other push rod 2252. When the other push rod 2252 extends, it fits precisely against another mating guide cone surface 22311 of the valve core 2231, thus forming a smooth closed-loop motion trajectory. In this way, the axial linear motion of the valve core 2231 is converted into the radial reciprocating motion of the push rod 2252, which greatly saves the valuable axial space inside the rotating component 22. By changing the slope of the guide cone 22311, the transmission ratio of the hydraulic feedback system can be easily adjusted, thereby changing the system's response sensitivity and increasing the equipment's flexibility.

[0041] like Figures 3 to 8 and Figure 11 As shown: The connecting flow channel 2251 is constructed as a damping channel; when the valve core 2231 is displaced by the impact of fluid pressure, the hydraulic medium is forced to flow in the connecting flow channel 2251 and generate viscous damping force, which is used to suppress the high-frequency oscillation of the valve core 2231 and maintain the dynamic stability of the adjustment process.

[0042] To address the potential high-frequency oscillation issue of valve core 2231 near critical pressure, this embodiment optimizes the fluid dynamics of the connecting channel 2251. The connecting channel 2251 is configured as a slender microporous channel or equipped with specialized throttling damping. When valve core 2231 experiences sudden displacement due to fluid pressure impact, the hydraulic medium is forced to flow rapidly within the narrow connecting channel 2251. Utilizing the viscous resistance effect of the liquid, significant fluid resistance is generated. This resistance is proportional to the square of the velocity. For slow pressure regulation, the resistance is minimal; for high-frequency pressure impacts, the resistance is extremely high. In marine conditions, influenced by pressure fluctuations in ship water supply pump stations and high-viscosity cargo oil media, the fluid often experiences severe pulsation. Effectively filtering out the high-frequency interference caused by fluid pulsation gives valve core 2231 a delayed and smooth action. This improves the dynamic stability of the equipment under harsh operating conditions, prevents sealing failure caused by valve core 2231 vibration, and extends the service life of the reset assembly 224.

[0043] like Figures 3 to 8 and Figure 11 As shown: Multiple arrayed throttling orifices 22312 are provided on the end of the flow channel 2232 near the liquid supply pipe 1; the throttling orifices 22312 are used to form multi-stage pressure drop in the initial stage of opening the pressure relief channel 222, and smooth the sudden change in flow rate during the pressure relief process.

[0044] If the flow rate is suddenly released at the moment the pressure relief channel 222 is first opened, it will cause a sharp drop in system pressure and result in violent fluctuations in rotational speed. In this embodiment, an array of throttling orifices 22312 is provided at the end of the flow channel 2232 of the valve core 2231 near the liquid supply pipe 1. As the valve core 2231 moves axially, these throttling orifices 22312 are not all exposed at once, but are connected to the liquid supply pipe 1 one by one. In the initial stage of opening, the fluid must pass through the small throttling orifices 22312, generating a large friction resistance and limiting the explosive growth of the diversion flow rate. This achieves a soft start in the pressure relief process and smooths the flow rate change curve. It avoids the instantaneous collapse of system pressure caused by the sudden opening of the bypass, ensures a smooth transition from acceleration mode to constant speed mode, and prevents nozzle speed nodding.

[0045] like Figure 3 , Figures 5 to 8 As shown: The reset component 224 is one or a combination of a helical spring, a disc spring, a wave spring or a pneumatic spring; the reset component 224 is coaxially sleeved on the outer periphery of the adjustment mechanism 223 or abuts against the end of the adjustment mechanism 223.

[0046] Considering the confined internal space and high-speed rotation of the tank washing machine, the selection and arrangement of the reset assembly 224 are crucial. This embodiment preferably uses one or a combination of helical springs, disc springs, wave springs, or pneumatic springs, extending axially along the rotating component 22. The reset assembly 224 is directly coaxially sleeved on the outer periphery of the adjusting mechanism 223 or abuts against its end. The spring force direction is opposite to the fluid pressure direction and on the same straight line, with no additional torque. Compared to radially arranged springs, axially arranged springs are least affected by centrifugal force, ensuring the stability of their elastic coefficient and preload at different speeds. The slender space inside the rotating component 22 is effectively utilized, reducing the radial dimension of the equipment and making it easier to pass through narrow tank washing openings. The accuracy of the threshold setting is ensured, preventing lateral bending or jamming of the spring due to centrifugal force, and ensuring the dual-mode switching point remains precise.

[0047] like Figures 3 to 8 As shown: The outlet of the pressure relief channel 222 is connected to the water outlet area downstream of the impeller 221 to discharge the diverted fluid.

[0048] The outlet of pressure relief channel 222 does not lead directly to the outside of the equipment, but rather connects to the water outlet area downstream of impeller 221. In this way, the high-pressure fluid that does not participate in driving impeller 221, after bypassing impeller 221, rejoins the main water flow. This avoids disorderly spraying of diverted fluid on the side of the equipment. In the deep, suspended operating environment of a ship's cargo oil tank, this not only prevents interference with the cleaning jet trajectory of the main nozzle, but also eliminates the additional reaction torque generated by direct lateral drainage, preventing the equipment from violently swinging and colliding inside the tank, thus preventing damage to the hull frame or the anti-corrosion coating of the inner wall, and ensuring the overall stability of the tank cleaning machine in its suspended state within the complex hull structure.

[0049] like Figures 3 to 8 As shown: The inner wall of the rotating component 22 is provided with an annular limiting step 226, which is used to limit the maximum axial displacement limit of the adjusting mechanism 223 in the adjusting state, and prevent the adjusting mechanism 223 from disengaging from or excessively compressing the reset component 224.

[0050] To prevent damage to the regulating mechanism 223 due to extreme high pressure, this embodiment incorporates an annular limiting step 226 machined into the inner wall of the rotating component 22. This limiting step 226 serves as the physical endpoint on the movement path of the regulating mechanism 223. When the regulating mechanism 223 is pushed to its maximum design stroke by excessive fluid pressure, its end face directly abuts against the limiting step 226, preventing further movement. This mechanical hard limit prevents the regulating mechanism 223 from slipping out of the guide groove or from over-compressing the reset assembly 224, causing spring coil failure. The maximum opening of the pressure relief channel 222 is limited, ensuring that the system retains a minimum back pressure under any extreme conditions, maintaining basic operational safety of the equipment.

[0051] like Figure 3 , Figure 5 , Figures 7 to 10 As shown: A gear reducer 211 is also provided between the nozzle assembly 21 and the rotating component 22.

[0052] Although the impeller 221's rotational speed is controlled at a constant speed, its physical rotational speed is still too fast for direct cleaning. Therefore, in this embodiment, a planetary gear reducer 211 is integrated between the nozzle assembly 21 and the rotating component 22. The gear reducer 211 includes a sun gear, gears, a ring gear, and a planet carrier. The sun gear is connected to the power output end of the impeller 221, the ring gear is relatively fixed, and the planet carrier is connected to the nozzle assembly 21. The planet carrier is equipped with multiple planetary gears that mesh with the sun gear and the ring gear to convert the high-speed rotation of the impeller 221 into low-speed, high-torque rotation of the nozzle assembly 21. Due to the gear reducer 211's strong load-bearing capacity and small size, it can output a huge driving torque, ensuring that the equipment does not jam even when thick sludge adheres to the outside of the nozzle, achieving stable and reliable 360-degree full-coverage cleaning.

[0053] The above embodiments only illustrate one or more implementations of the present invention, and their descriptions are relatively specific and detailed, but they should not be construed as limiting the scope of the present invention. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these all fall within the protection scope of the present invention. Therefore, the protection scope of the present invention should be determined by the appended claims.

Claims

1. A high-efficiency automatic tank cleaning device for oil tanker cargo tanks, comprising a liquid supply pipe and a nozzle assembly, characterized in that, It also includes a housing fitted around the periphery of the liquid supply pipe, and the nozzle assembly is rotatably mounted on the housing; The housing contains a rotatable rotating component, which is fitted around the outer periphery of the liquid supply pipe. An impeller, which is rotated by the impact of fluid, is fixedly installed inside the rotating component, and a pressure relief channel is provided on the rotating component. The pressure relief channel is constructed to draw out the fluid without passing through the impeller. The nozzle assembly is connected to the rotating component via a drive mechanism; The rotating component is also provided with an adjustment mechanism that is driven by the fluid pressure in the supply pipe to slide back and forth along the axis of the rotating component, and a reset component that provides a reverse biasing force to resist the adjustment mechanism. The displacement of the adjustment mechanism can control the opening and closing of the pressure relief channel. The adjustment mechanism is configured to keep the pressure relief channel closed when the fluid pressure is below a preset threshold, so that the rotation speed of the nozzle assembly increases as the pressure increases; when the fluid pressure exceeds the preset threshold, the sliding adjustment mechanism overcomes the bias force of the reset assembly to open the pressure relief channel, so as to divert the fluid and keep the rotation speed of the nozzle assembly within a preset constant range.

2. The high-efficiency automatic tank cleaning equipment for oil tanker cargo tanks according to claim 1, characterized in that, The regulating mechanism includes a valve core with a flow channel. When the fluid pressure is lower than a preset threshold, the solid part of the valve core blocks the pressure relief channel. When the fluid pressure exceeds the preset threshold, the valve core is displaced, causing the flow channel to connect the pressure relief channel with the fluid environment in the supply pipe, thereby implementing flow diversion.

3. The high-efficiency automatic tank cleaning equipment for oil tanker cargo tanks according to claim 2, characterized in that, The rotating component is equipped with a hydraulic feedback assembly; the hydraulic feedback assembly includes a connecting channel opened in the rotating component and a hydraulic medium filled in the connecting channel, as well as push rods with sliding seals at both ends of the connecting channel; one end of the two push rods acts on the hydraulic medium, and the other end abuts against different axial positions on the outer wall of the valve core, forming a hydraulic closed-loop linkage structure.

4. The high-efficiency automatic tank cleaning equipment for oil tanker cargo tanks according to claim 3, characterized in that, The outer wall of the valve core is provided with at least two guide cone surfaces; the guide cone surfaces cooperate with the abutting ends of the two push rods; when the valve core moves axially, the slope of the guide cone surfaces drives one of the push rods to retract into the connecting flow channel, while the hydraulic medium drives the other push rod to extend out of the connecting flow channel.

5. The high-efficiency automatic tank cleaning equipment for oil tanker cargo tanks according to claim 3, characterized in that, The connecting channel is constructed as a damping channel; when the valve core is displaced by the impact of fluid pressure, the hydraulic medium is forced to flow in the connecting channel and generate viscous damping force, which is used to suppress the high-frequency oscillation of the valve core and maintain the dynamic stability of the adjustment process.

6. The high-efficiency automatic tank cleaning equipment for oil tanker cargo tanks according to claim 2, characterized in that, The guide channel is provided with a plurality of arrayed throttling orifices at one end near the liquid supply pipe; the throttling orifices are used to form a multi-stage pressure drop in the initial stage of opening the pressure relief channel, smoothing the sudden change in flow rate during the pressure relief process.

7. The high-efficiency automatic tank cleaning equipment for oil tanker cargo tanks according to claim 1, characterized in that, The reset component is one or a combination of a helical spring, a disc spring, a wave spring, or a pneumatic spring; the reset component is coaxially sleeved on the outer periphery of the adjusting mechanism or abuts against the end of the adjusting mechanism.

8. The high-efficiency automatic tank cleaning equipment for oil tanker cargo tanks according to claim 1, characterized in that, The outlet of the pressure relief channel is connected to the water outlet area downstream of the impeller to discharge the diverted fluid.

9. The high-efficiency automatic tank cleaning equipment for oil tanker cargo tanks according to claim 1, characterized in that, The inner wall of the rotating component is provided with an annular limiting step, which is used to limit the maximum axial displacement limit of the adjusting mechanism in the adjusting state, and prevent the adjusting mechanism from disengaging from or excessively compressing the reset component.

10. The high-efficiency automatic tank cleaning equipment for oil tanker cargo tanks according to claim 1, characterized in that, A gear reduction gearbox is also provided between the nozzle assembly and the rotating component.

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