High-low pressure combined jet flow assisted ice breaking and cleaning system

Abstract

The invention relates to the field of polar region ship manufacturing, in particular to a high-low pressure combined jet flow auxiliary ice breaking and removing system which comprises a sharp-edge venturi spray pipe, the inner arc face of the sharp-edge venturi spray pipe is sequentially provided with an arc profile-shaped contraction section, a cylinder throat part and a diffusion section, and the position, connected to the inner arc face of the diffusion section in a sleeving mode, of a radial cylinder is provided with an elastic end part. Through an electromagnetic linkage mechanism of a magnetic ring coil and a magnetic block on a trigger end piece, a water diversion movable block and a water diversion static block are driven to generate relative displacement, rapid switching between a high-pressure jet mode and a low-pressure jet mode is achieved, action response is timely, operation is stable and reliable, and in the high-pressure mode, the magnetic block keeps a neutral state to drive the water diversion movable block and the water diversion static block to be accurately positioned; the counter bore and the middle ring flow hole form a straight-through type low-resistance flow channel, high-pressure water flow optimizes the flow state through the sharp-edge venturi spray pipe and accelerates the flow state, then strong-impedance ice conditions such as thick ice layers and ice ridges can be efficiently broken through the dynamic pressure impact and stress wave damage effect, and in a low-pressure mode, the magnetic ring coil adjusts the magnetic field to drive the magnetic block to deviate.

Description

Technical Field

[0001] This invention relates to the field of polar shipbuilding, specifically to a high-low pressure combined jet-assisted icebreaking and de-icing system. Background Technology

[0002] In scenarios such as polar waterway development, inland waterway transportation in high-altitude and frigid regions, and winter port operations, ice layers pose a significant threat to ship navigation safety, navigation efficiency, and port operational stability. Ice layers in polar and high-latitude frigid regions are characterized by their thickness, high density, high strength, and tendency to form ice ridges. These conditions, coupled with extreme low temperatures ranging from -60°C to 0°C and high wind speeds, further exacerbate the difficulty of icebreaking operations.

[0003] Traditional icebreaking operations mainly rely on the impact and compression of the icebreaker's hull structure. These icebreakers are usually equipped with heavy, reinforced bows and sides, using their huge displacement and kinetic energy to impact the ice layer and force it to break. However, this method has obvious limitations. First, the icebreaking efficiency is limited by the tonnage and speed of the hull. When facing thick ice layers or dense ice floes, repeated impacts and crushing are required, resulting in extremely high energy consumption and long operation cycles. Second, the rigid contact between the hull and the ice layer can easily cause wear and deformation of the hull structure, increasing ship maintenance costs. Third, traditional impact-based icebreaking methods are not suitable for thin ice layers, ice-slag mixtures, or ice adhering to the surface of the ship, and can easily cause problems such as wheel slippage and reduced propulsion efficiency. To make up for the shortcomings of traditional icebreaking technology, jet icebreaking technology has gradually become a research and application hotspot. Jet icebreaking is based on the impact force, shear force, and cavitation effect of high-pressure water flow. Water is pressurized by a high-pressure pump and then sprayed out through nozzles to form a high-speed jet that impacts the ice layer, causing stress concentration inside the ice layer and causing it to break.

[0004] Chinese invention patent publication number CN113022797B discloses a variable stern structure suitable for icebreaking operations at the stern of an icebreaker, including an icebreaking cone, an icebreaking reamer, and a water jet system. The icebreaking cone is detachably connected to the stern of the hull via a hydraulic cylinder, and several icebreaking cones are provided on the outer surface of the icebreaking cone. The icebreaking reamer is connected to a mounting groove on a reinforcing plate via a telescopic rotating assembly, and the reamer head extends from a guide hole on the icebreaking cone. A water pump in the water jet system is installed on the bow side and connected to a booster pump via a pipeline. The booster pump is connected to a high-speed water jet gun via a high-pressure water supply pipe, and the high-speed water jet gun is located on a support mechanism at the rear of the stern. This invention utilizes a combination of multiple structures for icebreaking, which not only ensures excellent continuous icebreaking capability for polar vessels stern-direction navigation, but also simultaneously achieves auxiliary ice removal and drag reduction, improving icebreaking efficiency and adapting to different navigation needs.

[0005] However, the jet system in the above structure adopts a single high-pressure jet design, which fails to achieve high and low pressure coordination and adaptation for ice layers of different thicknesses and intensities in the polar regions. When facing thick ice ridges with high strength, the jet impact force is difficult to effectively penetrate the ice layer, resulting in a significant lack of icebreaking capability. When facing thin ice layers or ice accumulation on the surface of ships and vessels, the excessively high jet pressure is likely to damage the hull structure and ship components. At the same time, a single jet beam is prone to diffusion and deviation in the high wind speed environment of the polar regions, leading to increased energy loss and a significant reduction in the effective icebreaking distance. Summary of the Invention

[0006] This invention addresses the technical problems existing in the prior art by providing a high-low pressure combined jet-assisted ice breaking and de-icing system.

[0007] The technical solution of this invention to solve the above-mentioned technical problems is as follows: A high-low pressure combined jet-assisted ice breaking and clearing system includes a sharp-edged Venturi nozzle. The inner arc surface of the sharp-edged Venturi nozzle is sequentially provided with an arc-shaped contraction section, a cylindrical throat, and a diffuser section. A radial cylinder is sleeved at one end of the inner arc surface of the diffuser section. The radial cylinder has an elastic end at the point where it is sleeved onto the inner arc surface of the diffuser section. The inner arc surface of the radial cylinder has a cavity groove. A magnetic ring coil is sleeved in the cavity groove of the radial cylinder. A high-pressure combined jet-assisted ice breaking and clearing system is connected to the inner arc surface of the radial cylinder on the side away from the sharp-edged Venturi nozzle. The high-pressure switching device includes a water-distributing movable block connected to the radial interior of the cylinder. One end face of the water-distributing movable block is provided with a snap-fit ​​protrusion. A connecting joint is provided in the middle of the inner arc surface of the water-distributing movable block. A countersunk hole is provided between the connecting joint and the snap-fit ​​protrusion. A water-distributing stationary block is movably connected to the water-distributing movable block through the snap-fit ​​protrusion on one end face. A snap-fit ​​groove is provided on the side of the water-distributing stationary block near the water-distributing movable block. The snap-fit ​​protrusion is fixedly snapped into the snap-fit ​​groove. A central flow hole is provided in the middle of one side surface of the water-distributing stationary block. The central flow hole is adapted to the countersunk hole.

[0008] In a preferred embodiment, a trigger end piece is movably engaged at the middle connecting joint of the water-distributing block. One end of the trigger end piece extending radially from the cylinder is provided with an elastic support arm. The elastic support arm has two ends, and magnetic blocks are provided on the surface of both ends of the elastic support arm. The magnetic blocks are adapted to the outer magnetic ring coil.

[0009] In a preferred embodiment, the outer diameter of the water-distributing static block is adapted to the inner diameter of the radial cylinder, the magnetic blocks on the upper and lower sides are placed opposite each other, a flow cavity is provided between the water-distributing moving block and the inner diameter of the radial cylinder, the flow cavity is related to the distance between the magnetic blocks in the magnetic ring coil, and one end face of the water-distributing static block is slidably attached to one end face of the radial cylinder.

[0010] In a preferred embodiment, a hinge end is provided on one side of the outer arc surface of the radial cylinder. One side of the hinge end is placed outside one end of the diffuser section. A corrugated sleeve is connected to the surface of the hinge end. A spring is fixedly installed on the inner arc surface of the corrugated sleeve. One end of the spring is fixedly connected to the hinge end of the radial cylinder.

[0011] In a preferred embodiment, the other end of the spring is connected to the surface of the corrugated sleeve, the end face of the corrugated sleeve away from the hinge end is fixedly installed on the sharp-edged venturi nozzle, the outer arc surface of the corrugated sleeve is fitted with a heat-conducting coil, and the corrugated sleeve is placed on the outer arc surface of the high-pressure switching device.

[0012] In a preferred embodiment, a segmented jet assembly is threaded onto one side of the hinge end of the outer arc surface of the radial cylinder. The segmented jet assembly includes an integral jet connector connected to the outer arc surface of the radial cylinder. The integral jet connector is divided into a mid-section high-pressure module and a peripheral low-pressure module.

[0013] In a preferred embodiment, the middle section of the integrated jet connector is provided with a jet passage cavity A, and a high-pressure nozzle with a conical diameter is fixedly connected to the inner arc surface of the jet passage cavity A. A conical anti-backflow screen is provided on one side of the inner arc surface of the high-pressure nozzle with a conical anti-backflow screen having elastic deformation characteristics.

[0014] In a preferred embodiment, a jet cavity B is provided between the integrated jet connector and the jet cavity A. A flow-guiding hole is provided on the side of the integrated jet connector near the jet cavity B. An annular arc segment is provided on the outer arc surface of the integrated jet connector, and a flow-rectifying cavity is provided in the inner arc surface of the annular arc segment.

[0015] In a preferred embodiment, the rectifying cavity is connected to the drainage hole, the annular arc segment is made of deformable material, one side of the outer arc surface of the annular arc segment is adapted to abut against the corrugated sleeve, a low-pressure injection port is provided at the concave surface of the annular arc segment, the high-pressure nozzle with a conical diameter in the injection cavity A corresponds to the middle ring flow hole in the middle of the water distribution stationary block, and the flow cavity between the water distribution moving block and the radial cylinder is adapted to the injection cavity B.

[0016] The beneficial effects of this invention are: Through the electromagnetic linkage mechanism between the magnetic ring coil and the magnetic block on the trigger end, the relative displacement of the water-distributing moving block and the water-distributing stationary block is driven, realizing the rapid switching between high-pressure jet and low-pressure jet modes. The action response is timely and the operation is stable and reliable. In high-pressure mode, the magnetic block remains in a neutral state, driving the water-distributing moving block and the water-distributing stationary block to be precisely positioned, so that the sinker and the middle ring flow hole form a straight-through low-resistance flow channel. After the high-pressure water flow is optimized and accelerated through the sharp-edged Venturi nozzle, it can efficiently break through thick ice layers, ice ridges and other strong resistance ice conditions by means of dynamic pressure impact and stress wave destruction effect. In low-pressure mode, the magnetic ring coil adjusts the magnetic field to drive the magnetic block to deflect, and realizes water flow diversion through flow channel misalignment. It is suitable for thin ice layer cleaning, removal of ice attached to ships and wheels and snow melting needs. At the same time, it can form a continuous water film at the interface between the ship and the ice layer, effectively reducing navigation resistance.

[0017] The sharp-edged Venturi nozzle, with its three-section structure consisting of a converging section with a circular profile, a cylindrical throat, and a diffuser section, achieves smooth acceleration and regular flow of water, minimizing eddy current losses and significantly enhancing the concentration of high-pressure water kinetic energy. When impacting the ice layer, it can quickly induce the initiation and expansion of internal micro-cracks, greatly enhancing ice-breaking efficiency. The conical anti-backflow screen inside the high-pressure nozzle remains open under the impact of high-pressure water flow, ensuring smooth water flow and preventing external ice debris from entering the flow channel, avoiding efficiency reduction caused by flow channel blockage, and ensuring the continuity and stability of high-pressure ice breaking.

[0018] A coordinated rectification and regulation system is formed by the rectification cavity, corrugated sleeve and spring. The water flow is regulated by the rectification cavity, which effectively avoids the defects of traditional low-pressure jets such as easy diffusion and large energy loss. The annular arc section is made of deformable material. Its expansion degree is positively correlated with the water flow pressure. It can adaptively adapt to low-pressure water flow of different flow rates. The elastic force of the spring stabilizes the jet pressure and avoids the impact of water flow fluctuation on the jet effect. At the same time, the buffering effect of the spring can reduce the interference of the high wind speed environment in the polar region on the jet trajectory, improve the effective range and coverage uniformity of the low-pressure jet, and take into account both the ice removal effect and drag reduction efficiency.

[0019] The heat-conducting coil on the outer arc surface of the corrugated sleeve can access the waste heat of the ship's engine to heat and insulate key components and flow channels, preventing components from freezing and failing due to low temperatures. In addition, the elastic end at the connection between the sharp-edged venturi nozzle and the radial cylinder can effectively absorb the structural thermal expansion and contraction stress at low temperatures, avoiding cracking of rigid connections, while enhancing the sealing of the connection and preventing freezing after water leakage. Attached Figure Description

[0020] Figure 1 This is a structural diagram of the bow section of the high-low pressure combined jet-assisted icebreaking front end of the present invention; Figure 2 This is a three-dimensional view showing the overall interior of the cross-section of the sharp-edged Venturi nozzle in this invention; Figure 3This is a schematic diagram of the front end of the segmented jet assembly abutting against the corrugated sleeve in this invention; Figure 4 This is a schematic diagram of the internal structure of the high-voltage switching device in this invention. Figure 5 This is a diagram illustrating the positional relationship between the magnetic ring coil and the magnetic block on the elastic support arm in this invention; Figure 6 This is a schematic cross-sectional view of the sharp-edged Venturi nozzle and the corrugated sleeve in this invention. Figure 7 This is a schematic diagram of the disassembled structure of the water-dividing moving block and the water-dividing stationary block in this invention; Figure 8 This is a schematic cross-sectional view of the integrated jet connector in this invention; Figure 9 This is a three-dimensional structural diagram of the injection cavity A and injection cavity B of the present invention; Figure 10 This is a schematic diagram showing the overall structure of the sharp-edged venturi nozzle of the present invention.

[0021] In the diagram: 1. Sharp-edged Venturi nozzle; 101. Circular arc-shaped contraction section; 102. Cylindrical throat; 103. Diffusion section; 2. Radial cylinder; 201. Elastic end; 202. Hinge end; 3. Magnetic ring coil; 4. High-pressure switching device; 41. Water distribution moving block; 411. Snap-fit ​​protrusion; 412. Connecting joint; 413. Countersunk hole; 42. Water distribution stationary block; 421. Middle ring flow hole; 43. Trigger end piece; 431. Elastic support arm; 432. Magnetic block; 44. Flow chamber; 5. Corrugated sleeve; 6. Spring; 7. Heat-conducting coil; 8. Segmented jet assembly; 81. Integrated jet connector; 811. Jet passage A; 812. Jet passage B; 813. Drain hole; 814. Annular arc section; 815. Rectifying cavity; 82. Conical high-pressure nozzle; 821. Conical anti-backflow screen; 83. Low-pressure jet port. Detailed Implementation

[0022] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0023] As attached Figure 1-10As shown, this embodiment provides a high-low pressure combined jet-assisted ice breaking and clearing system, including a water-distributing moving block 41 connected to the interior of a radial cylinder 2. One end face of the water-distributing moving block 41 is provided with a snap-fit ​​protrusion 411, and a connecting joint 412 is provided in the middle of the inner arc surface of the water-distributing moving block 41. A countersunk hole 413 is provided between the connecting joint 412 and the snap-fit ​​protrusion 411. A water-distributing stationary block 42 is movably connected to the water-distributing moving block 41 through the snap-fit ​​protrusion 411 on one end face. The water-distributing stationary block 42 is close to the water-distributing moving block 41. A snap-fit ​​groove is provided on one side of block 41, and the snap-fit ​​protrusion 411 is fixedly snapped into the snap-fit ​​groove. A middle ring flow hole 421 is provided in the middle of one side surface of the water-dividing static block 42. The middle ring flow hole 421 is adapted to the countersunk hole 413. A segmented jet assembly 8 is threadedly sleeved on one side of the hinge end 202 of the outer arc surface of the radial cylinder 2. The segmented jet assembly 8 includes an integrated jet connector 81 connected to the outer arc surface of the radial cylinder 2. The integrated jet connector 81 is divided into a middle high-pressure module and a peripheral low-pressure module.

[0024] The middle section of the integrated jet connector 81 is provided with a jet passage cavity A811. A high-pressure nozzle 82 with a conical diameter is fixedly connected to the inner arc surface of the jet passage cavity A811. A conical anti-backflow screen 821 is provided on one side of the inner arc surface of the high-pressure nozzle 82. The conical anti-backflow screen 821 has elastic deformation characteristics.

[0025] according to Figure 2 , Figure 4 and Figure 5 When the ice layer detection system reports strong impedance ice conditions such as thick polar ice layers (over 0.5m) or ice ridges, the system automatically triggers the high-pressure jet mode. At this time, the controller sends a specific current of constant amplitude to the magnetic ring coil 3, so that a uniform and stable radial magnetic field is formed inside the coil. Under the action of this magnetic field, the magnetic blocks 432 symmetrically arranged at the upper and lower ends of the trigger end 43 are subjected to electromagnetic forces of equal magnitude and opposite direction, and finally maintain a strictly neutral state in the middle of the magnetic field. This neutral posture is transmitted through the rigid connection between the trigger end 43 and the water-dividing moving block 41 and the connection 412, which drives the water-dividing moving block 41 to maintain the reference state synchronously, and then pulls the water-dividing stationary block 42 to stabilize at the same position as the inner wall of the radial cylinder 2. At this time, the outer circular surface of the water-dividing stationary block 42 is tightly attached to the inner circular surface of the radial cylinder 2, ensuring that the water flow will not leak from the gap.

[0026] Although the flow cavity 44 between the water-distributing moving block 41 and the inner diameter of the radial cylinder 2 is in a naturally open state, due to the reference positioning of the water-distributing stationary block 42, the water flow will preferentially choose the straight channel with the least resistance due to the difference in flow channel resistance. At this time, the middle ring flow hole 421 in the middle of one side surface of the water-distributing stationary block 42 and the countersunk hole 413 of the water-distributing moving block 41 are aligned to form a straight high-pressure flow channel with no bends and low resistance. It is worth noting that the water-distributing moving block 41 forms a circumferential limit with the locking protrusion 411 on one side end face and the locking groove of the water-distributing stationary block 42, ensuring that the two will not rotate relative to each other under the impact of high-pressure water flow, further ensuring the stable conduction of the high-pressure flow channel.

[0027] After entering the system from the inlet, the high-pressure water is pressurized to 20-400MPa by a high-pressure pump (dynamically adjusted according to ice thickness). It then flows through the arc-shaped contraction section 101 of the sharp-edged Venturi nozzle 1. This contraction section adopts a smooth transition arc-shaped design, which can effectively avoid the generation of eddies during the contraction process and achieve smooth acceleration of the water flow. The water then enters the cylindrical throat 102, where the flow velocity is further increased to the speed of sound under the constraint of the throat, forming a high-speed and stable columnar flow. After the diffusion effect of the diffuser section 103, the water pressure is partially restored and the flow state is stabilized. Finally, it enters the radial cylinder 2 in a uniform high-speed flow state. The high-pressure water entering the radial cylinder 2 passes through the countersunk hole 413 of the water distribution moving block 41 and the middle ring flow hole 421 of the water distribution stationary block 42 in sequence, and is directly injected into the jet passage A811 in the middle section of the integrated jet connector 81. Finally, it is ejected at high speed by the cone-diameter high-pressure nozzle 82 to form a high-energy jet beam.

[0028] During this process, the conical anti-backflow screen 821 set on the inner arc surface of the high-pressure nozzle 82 overcomes its own elastic pre-tightening force and remains fully open due to the positive impact of the high-pressure water flow. This provides an unobstructed flow channel for the high-pressure water flow and effectively prevents broken ice chips and ice crystals from entering the flow channel, avoiding blockage or component wear. At the same time, when the high-speed high-pressure jet impacts the ice layer, it achieves efficient ice breaking through a triple core mechanism: Dynamic pressure impact and stress wave damage: The jet instantly generates a dynamic pressure load far exceeding the tensile and compressive strength of the ice body on a very small contact area. The impact energy propagates into the ice body in the form of compression waves and shear waves. When the compression wave encounters bubbles, cracks or ice layer boundaries in the ice body, it is reflected to form a tensile wave. Taking advantage of the fact that the tensile strength of the ice body is only 1 / 10 to 1 / 5 of the compressive strength, it quickly induces the initiation and penetration of internal microcracks, fundamentally destroying the structural integrity of the ice body. The "water wedge" effect of shearing and erosion: After the jet impacts the ice surface, the horizontally flowing water layer forms a "water wedge", generating extremely high shear stress around the impact point, continuously peeling off ice crystal particles and expanding cracks. Especially for thick ice layers that have been pre-cracked by stress waves, it can quickly form through grooves. Thermodynamic auxiliary effect: The jet water temperature is maintained above 0℃. When it impacts the ice surface or seeps into cracks, it releases a small amount of heat, which accelerates local melting, slightly reduces the strength of the ice, and assists in crack propagation. Although this effect is weaker than mechanical damage, it can effectively improve icebreaking efficiency in the low-temperature polar environment.

[0029] Combination Figure 7 and Figure 10 A trigger end piece 43 is movably engaged at the middle connecting joint 412 of the water-distributing moving block 41. One end of the trigger end piece 43 extending into the radial cylinder 2 is provided with an elastic support arm 431. The elastic support arm 431 has two ends, upper and lower. Both ends of the elastic support arm 431 are provided with magnetic blocks 432. The magnetic blocks 432 are adapted to the outer magnetic ring coil 3. The outer diameter of the water-distributing stationary block 42 is adapted to the inner diameter of the radial cylinder 2. The upper and lower magnetic blocks 432 are placed opposite each other. A flow cavity 44 is provided between the water-distributing moving block 41 and the inner diameter of the radial cylinder 2. The flow cavity 44 is related to the distance between the magnetic blocks 432 in the magnetic ring coil 3. One end face of the water-distributing stationary block 42 slides and fits against one end face of the radial cylinder 2.

[0030] A jet cavity B812 is provided between the integrated jet connector 81 and the jet cavity A811. A flow guide hole 813 is provided on the side of the integrated jet connector 81 near the jet cavity B812. An annular arc section 814 is provided on the outer arc surface of the integrated jet connector 81. A flow rectifier 815 is provided in the inner arc surface of the annular arc section 814. The flow rectifier 815 is connected to the flow guide hole 813. The annular arc section 814 is made of deformable material. One side of the outer arc surface of the annular arc section 814 is abutted and adapted to the corrugated sleeve 5. A low-pressure jet nozzle 83 is provided at the concave surface of the annular arc section 814. The high-pressure nozzle 82 with a conical diameter in the jet cavity A811 corresponds to the middle ring flow hole 421 in the middle of the water distribution block 42. The flow cavity 44 between the water distribution block 41 and the radial cylinder 2 is adapted to the jet cavity B812.

[0031] When facing thin ice layers such as less than 0.5m, ice accumulation on the surface of ships, or when it is necessary to reduce the friction coefficient of ice to reduce drag during navigation, the system switches to low-pressure jet mode. At this time, the controller adjusts the current direction and current intensity of the magnetic ring coil 3 to generate a non-uniform bias magnetic field. The magnetic field intensity exhibits a distribution characteristic of unilateral enhancement and unilateral weakening along the radial direction. Under the action of this non-uniform magnetic field, the magnetic blocks 432 at the upper and lower ends of the trigger end 43 are subjected to unbalanced electromagnetic attraction forces, and thus shift directionally to the side with stronger magnetic field intensity and are firmly attracted. The offset of the magnetic blocks 432 is controlled by the current intensity to ensure the accuracy of subsequent flow channel switching.

[0032] The offset of the magnetic block 432 is transmitted to the trigger end 43 through the elastic support arm 431, causing the trigger end 43 to deflect around the connecting joint 412. This deflection force further drives the water-distributing moving block 41 to undergo a controllable displacement radially upward or downward inside the flow cavity 44. The displacement of the water-distributing moving block 41 directly causes the central countersunk hole 413 to be misaligned with the central flow hole 421 of the water-distributing stationary block 42, blocking the original high-pressure straight flow channel. Since the water-distributing stationary block 42 and the inner wall of the radial cylinder 2 always remain in contact, the water flow cannot pass through the high-pressure flow channel. At the same time, the displacement of the water-distributing moving block 41 will compress the local space of the flow cavity 44, causing a slight change in the water pressure inside the flow cavity 44. Under the dual action of pressure difference and flow channel blockage, the water flow is forced to change direction and slowly flow along the annular gap between the water-distributing stationary block 42 and the inner wall of the radial cylinder 2, eventually flowing into the jet passage B812 of the integrated jet connector 81. During this process, the elastic deformation characteristics of the elastic support arm 431 can buffer the impact force caused by the displacement of the magnetic block 432, and avoid rigid collision damage to the components.

[0033] The low-pressure water flow entering the jet cavity B812 passes through its circumferentially evenly distributed drainage holes 813 and simultaneously enters the rectifying cavity 815 of the annular arc section 814. Since the rectifying cavity 815 is a closed cavity structure, the water flow continuously accumulates inside. As the water volume increases, the water pressure inside the cavity gradually rises. The annular arc section 814 is made of a low-temperature resistant deformable elastic material, which will slowly expand outward under the action of water pressure. Its outer arc surface gradually contacts and squeezes the inner wall of the corrugated sleeve 5, thereby pushing the spring 6 on the inner arc surface of the corrugated sleeve 5 to undergo axial compression. This process not only realizes the pressure energy storage of the low-pressure water flow, but also completes the flow regulation and eliminates the water flow turbulence through the slow flow of water in the rectifying cavity 815 and the constraint of the cavity wall.

[0034] When the water pressure inside the rectifier cavity 815 reaches a preset threshold, the elastic deformation of the annular arc segment 814 reaches its limit, and the low-pressure jet nozzle 83 on its inner side fully opens. The regulated low-pressure water flow is ejected in a uniform dual-channel jet pattern, achieving a triple function: Thin ice layer removal: Low-pressure jets, through gentle impact and diffuse scouring, combined with the melting effect of water temperature, quickly remove thin ice layers below 0.5m and ice buildup on the ship and wheels without damaging the hull. Snow melting: The combined effect of jet water temperature and impact rapidly melts the snow covering the ice sheet surface, preventing the snow from compacting and forming a hard ice shell, while also reducing the obstruction of the jet effect by the snow. Drag Reduction: The low-pressure jet forms a continuous and stable water film at the interface between the hull and ice / ice fragments, transforming the original solid-solid friction into solid-liquid-solid friction. This reduces the friction coefficient between ice and ice, and between ice and the ship, by 10%-20% (with a reduction of approximately 6% in the dry and wet friction coefficient between the hull and ice, and a reduction of 21.4%-57.1% in the friction coefficient between the hull and dry / wet snow). Simultaneously, the jet actively guides ice fragments towards the sides of the hull or the rear of the ship through preset angles and directions, imparting additional kinetic energy to the ice fragments and accelerating their expulsion, thus reducing "ice blockage" at the bow. Model tests verify that activating the low-pressure jet system reduces the average ice resistance, and the drag reduction effect on snow-covered ice is improved compared to uncovered ice. like Figure 8 After the water flows into the rectifying cavity 815 through the inlet hole 813, it will first form a slow vortex circulation inside the cavity. During the circulation process, the turbulent flow clusters in the water will collide and dissolve with each other, achieving the initial rectification of the flow pattern. At the same time, the inner wall of the rectifying cavity 815 adopts a smooth arc design, which can avoid the water flow from stagnating or creating vortex dead angles inside the cavity, further improving the rectification effect of the flow pattern and avoiding the problem of uneven spraying caused by water turbulence.

[0035] Subsequently, the pressure generated by the regulated water flow drives the annular arc segment 814 to expand outward. The degree of expansion is related to the water flow pressure. When the water flow rate increases, the pressure inside the cavity increases, the expansion of the annular arc segment 814 increases, and the volume of the rectifier cavity 815 expands synchronously, which can accommodate more water flow. When the water flow rate decreases, the expansion decreases accordingly, and the volume contracts synchronously, thereby achieving adaptive adaptation to low-pressure water flow of different flow rates and ensuring the stability of the jet output.

[0036] When the water pressure in the rectifier cavity 815 reaches the preset value, the annular arc section 814 expands to its maximum volume. At this time, the low-pressure injection port 83 is fully opened, and the regulated low-pressure water flow is ejected through the preset channel. Throughout the injection process, the spring 6 remains in a compressed state, and the elastic restoring force it generates continuously acts on the outer arc surface of the annular arc section 814, forming a constraint force opposite to the direction of the water pressure. When the water pressure fluctuates and increases, the compression of the spring 6 increases, and the constraint force increases simultaneously, which can suppress the further expansion of the annular arc section 814 and prevent the injection pressure from being too high. When the water pressure fluctuates and decreases, the compression of the spring 6 decreases, and the constraint force decreases simultaneously. The annular arc section 814 maintains a stable expansion state under the action of the remaining water pressure, preventing the injection pressure from being too low, thereby achieving dynamic balance and stability of the injection pressure.

[0037] according to Figure 3 , Figure 8 and Figure 9A hinge end 202 is provided on one side of the outer arc surface of the radial cylinder 2. One side of the hinge end 202 is placed outside one end of the diffuser section 103. A corrugated sleeve 5 is connected to the surface of the hinge end 202. A spring 6 is fixedly installed on the inner arc surface of the corrugated sleeve 5. One end of the spring 6 is fixedly connected to the hinge end 202 of the radial cylinder 2, and the other end of the spring 6 is connected to the surface of the corrugated sleeve 5. The end face of the corrugated sleeve 5 away from the hinge end 202 is fixedly installed on the sharp-edged venturi nozzle 1. A heat-conducting coil 7 is sleeved on the outer arc surface of the corrugated sleeve 5. The corrugated sleeve 5 is placed on the outer arc surface of the high-pressure switching device 4.

[0038] For extreme low-temperature environments ranging from -60℃ to 0℃ in polar regions, the heat-conducting coil 7, which is sleeved on the outer arc surface of the corrugated sleeve 5, is made of copper alloy with a high thermal conductivity. It is connected to the cooling circulation system of the ship's engine through pipelines, which can efficiently transfer the waste heat generated during engine operation to the heat-conducting coil 7. This continuously heats and insulates the corrugated sleeve 5, the internal spring 6, and the surrounding flow channels, keeping the temperature of related components and water flow above 0℃. This prevents components from freezing and water flow from solidifying and failing due to low temperatures. At the same time, the heat-conducting coil 7 adopts a spiral winding design, which can increase the contact area with the corrugated sleeve 5, improve heat exchange efficiency, and eliminate the need for additional heating devices, effectively reducing system energy consumption.

[0039] The conical anti-backflow screen 821 inside the high-pressure nozzle 82 has a bidirectional elastic reset function. After the system stops and loses the impact of the high-pressure water flow, the backflow screen will automatically close under its own elastic restoring force to block the nozzle channel. This design not only prevents the water remaining inside the nozzle from flowing back into the flow channel and freezing, but also blocks external ice chips and ice crystals from entering the nozzle, thus avoiding nozzle blockage.

[0040] like Figure 1 , Figure 2 , Figure 3 and Figure 6 As shown, the nozzle includes a sharp-edged venturi nozzle 1. The inner arc surface of the sharp-edged venturi nozzle 1 is provided with a circular arc profile contraction section 101, a cylindrical throat 102 and a diffuser section 103 in sequence. A radial cylinder 2 is sleeved at one end of the inner arc surface of the diffuser section 103. An elastic end 201 is provided at the point where the radial cylinder 2 is sleeved to the inner arc surface of the diffuser section 103. A cavity is provided on the inner arc surface of the radial cylinder 2. A magnetic ring coil 3 is sleeved in the cavity of the radial cylinder 2. A high-pressure switching device 4 is connected in the inner arc surface of the radial cylinder 2 on the side away from the sharp-edged venturi nozzle 1.

[0041] The nozzle's inner arc surface is sequentially configured with a circular arc-shaped contraction section 101, a cylindrical throat 102, and a diffuser section 103. This three-section integrated structure can prevent eddy current losses during water flow. The circular arc-shaped contraction section 101 adopts a smooth transition curve design, which can more gently compress the water flow cross section and reduce water flow impact losses. The cylindrical throat 102 has a constant diameter structure, which enhances the water flow velocity region. The diffuser section 103 achieves partial recovery of water flow pressure and flow stability through a gradually expanding diameter design.

[0042] When the water enters the nozzle, it first flows through the arc-shaped contraction section 101, where the cross-sectional area of ​​the flow channel gradually decreases. According to the continuous water flow velocity, it increases synchronously to achieve initial acceleration. After entering the cylindrical throat 102, the cross-sectional area of ​​the flow channel remains constant, and the water flow velocity reaches its peak to form a high-speed and stable columnar flow. This flow state can retain the kinetic energy of the water to the greatest extent, providing a basis for the dynamic pressure impact and stress wave damage of the subsequent high-pressure jet. The high-speed water flow passes through the diffuser section 103, where the cross-sectional area of ​​the flow channel gradually expands, the water flow velocity slowly decreases, and the pressure is partially restored. The flow state changes from high-speed turbulence to stable laminar flow, avoiding water flow impact loss in the subsequent high-pressure switching device 4 due to flow turbulence, and ensuring that the water flow enters the radial cylinder 2 in a uniform and stable state.

[0043] The sharp-edge design reduces the risk of low-temperature water flow adhering to and freezing on the inner wall of the nozzle. At the same time, the elastic potential energy of the elastic end 201 at one end of the radial cylinder 2 can reduce the frictional resistance between the water flow and the pipe wall. In addition, the elastic end 201 can absorb the thermal expansion and contraction stress caused by temperature changes between the nozzle and the cylinder, avoiding structural cracking of the rigid connection under extreme low temperatures, ensuring the sealing and structural stability of the flow channel, and reducing the problem of local freezing caused by insufficient frictional heat generation of water flow under polar low temperatures. In addition, the high-pressure water flow accelerated by the nozzle has a significantly increased kinetic energy density, which can form instantaneous high pressure more quickly when impacting the ice layer, enhancing the dynamic pressure impact and stress wave destruction effect, and adapting to the icebreaking needs of thick polar ice layers, ice ridges and other strong resistance ice conditions.

Claims

1. A high-low pressure combined jet flow assisted ice breaking and ice removing system, comprising: A sharp-edged venturi nozzle (1) is characterized in that the inner arc surface of the sharp-edged venturi nozzle (1) is provided with a circular arc profile contraction section (101), a cylindrical throat (102) and a diffuser section (103) in sequence. A radial cylinder (2) is sleeved on one end of the inner arc surface of the diffuser section (103). An elastic end (201) is provided at the point where the radial cylinder (2) is sleeved on the inner arc surface of the diffuser section (103). A cavity is provided on the inner arc surface of the radial cylinder (2). A magnetic ring coil (3) is sleeved in the cavity of the radial cylinder (2). A high-pressure switching device (4) is connected to the inner arc surface of the radial cylinder (2) away from the sharp-edged Venturi nozzle (1). The high-pressure switching device (4) includes a water-dividing block (41) connected to the interior of the radial cylinder (2). One end face of the water-dividing block (41) is provided with a snap-fit ​​protrusion (411). A connecting joint (412) is provided in the middle of the inner arc surface of the water-dividing block (41). A countersunk hole (413) is provided between the connecting joint (412) and the snap-fit ​​protrusion (411). The water-dividing moving block (41) is movably connected to the water-dividing stationary block (42) through the snap-fit ​​protrusion (411) on one side end face. The water-dividing stationary block (42) has a snap-fit ​​groove on the side near the water-dividing moving block (41). The snap-fit ​​protrusion (411) is fixedly snapped into the snap-fit ​​groove. A central flow hole (421) is provided in the middle of one side surface of the water-dividing stationary block (42). The central flow hole (421) is adapted to the countersunk hole (413).

2. The high-low pressure combined jet flow auxiliary ice breaking and cleaning system according to claim 1, characterized in that, The middle connecting joint (412) of the water-dividing block (41) is movably connected to a trigger end piece (43). The trigger end piece (43) extends radially to one end of the cylinder (2) and is provided with an elastic support arm (431). The elastic support arm (431) has two ends, and the surfaces of the elastic support arm (431) at both ends are provided with magnetic blocks (432). The magnetic blocks (432) are adapted to the outer magnetic ring coil (3).

3. The high-low pressure combined jet flow auxiliary ice breaking and cleaning system according to claim 2, characterized in that, The outer diameter of the water-dividing static block (42) is adapted to the inner diameter of the radial cylinder (2). The magnetic blocks (432) on the upper and lower sides are placed opposite each other. A flow cavity (44) is provided between the water-dividing moving block (41) and the inner diameter of the radial cylinder (2). The flow cavity (44) is related to the distance between the magnetic block (432) in the magnetic ring coil (3). One end face of the water-dividing static block (42) slides and fits against one end face of the radial cylinder (2).

4. The high-low pressure combined jet flow auxiliary ice breaking and cleaning system according to claim 1, characterized in that, The radial cylinder (2) has a hinge end (202) on one side of its outer arc surface. One side of the hinge end (202) is placed outside one end of the diffuser section (103). A corrugated sleeve (5) is connected to the surface of the hinge end (202). A spring (6) is fixedly installed on the inner arc surface of the corrugated sleeve (5). One end of the spring (6) is fixedly connected to the hinge end (202) of the radial cylinder (2).

5. The high-low pressure combined jet-assisted ice breaking and de-icing system according to claim 4, characterized in that, The other end of the spring (6) is connected to the surface of the corrugated sleeve (5). The side of the corrugated sleeve (5) away from the hinge end (202) is fixedly installed on the sharp-edged Venturi nozzle (1). The outer arc surface of the corrugated sleeve (5) is fitted with a heat-conducting coil (7). The corrugated sleeve (5) is placed on the outer arc surface of the high-pressure switching device (4).

6. The high-low pressure combined jet-assisted ice breaking and de-icing system according to claim 4, characterized in that, The segmented jet assembly (8) is threaded onto one side of the hinge end (202) of the outer arc surface of the radial cylinder (2). The segmented jet assembly (8) includes an integral jet connector (81) connected to the outer arc surface of the radial cylinder (2), and the integral jet connector (81) is divided into a mid-section high-pressure module and a peripheral low-pressure module.

7. A high-low pressure combined jet-assisted ice-breaking and de-icing system according to claim 6, characterized in that, The integrated jet connector (81) has a jet passage cavity A (811) in the middle section. A high-pressure nozzle (82) with a conical diameter is fixedly connected to the inner arc surface of the jet passage cavity A (811). A conical anti-backflow screen (821) is provided on one side of the inner arc surface of the high-pressure nozzle (82). The conical anti-backflow screen (821) has elastic deformation characteristics.

8. The high-low pressure combined jet-assisted ice breaking and de-icing system according to claim 7, characterized in that, A jet cavity B (812) is provided between the integrated jet connector (81) and the jet cavity A (811). A flow-guiding hole (813) is provided on the side of the integrated jet connector (81) near the jet cavity B (812). An annular arc segment (814) is provided on the outer arc surface of the integrated jet connector (81). A flow-rectifying cavity (815) is provided in the inner arc surface of the annular arc segment (814).

9. A high-low pressure combined jet-assisted ice-breaking and de-icing system according to claim 8, characterized in that, The rectifying cavity (815) is connected to the drainage hole (813). The annular arc segment (814) is made of deformable material. The outer arc surface of the annular arc segment (814) is adapted to abut against the corrugated sleeve (5). The inner concave surface of the annular arc segment (814) is provided with a low-pressure injection port (83). The cone-diameter high-pressure nozzle (82) in the injection cavity A (811) corresponds to the middle ring flow hole (421) in the middle of the water-dividing static block (42). The flow cavity (44) between the water-dividing moving block (41) and the radial cylinder (2) is adapted to the injection cavity B (812).

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