Expander converging assembly for towing and expanding underwater equipment

Abstract

The utility model relates to the technical field of marine seismic exploration equipment components, in particular to an expander convergence component for towing and expanding underwater equipment, which comprises a support A, a support B and a main screw, the support A consists of an outer plate component and a lifting lug component, the outer plate component comprises two outer side vertical plates distributed in mirror symmetry, and the lifting lug component is arranged on the outer side vertical plates. The lifting lug assembly comprises two bearing lifting lugs which are arranged in parallel, the two bearing lifting lugs are welded and fixed between the inner side walls of the outer side vertical plates at equal intervals in the vertical direction, and the outer side walls of the bearing lifting lugs and the inner side walls of the outer side vertical plates are in full-circle fillet weld connection to form a bidirectional force conduction interface; the beneficial effects are that the asymmetric force conduction path is optimized: the layout of the double lifting lugs of the support A and the three lifting lugs of the support B are combined with 30-degree phase difference staggered assembly to form a space staggered mechanical frame, loads are dispersed through the asymmetric force conduction path, stress concentration is effectively avoided, and the anti-fatigue performance of the whole structure is improved.

Description

Technical Field

[0001] This utility model relates to the technical field of marine seismic exploration equipment components, specifically an extender assembly for towing and extending underwater equipment. Background Technology

[0002] Currently, in the field of underwater equipment towing and extension, traditional assembly components mostly adopt symmetrical structural designs, which have the following shortcomings: Low load transfer efficiency: Conventional lifting lug layouts are mostly symmetrically distributed, making it difficult to adapt to the multi-directional force requirements in complex underwater environments. This results in the inefficient synchronous transmission of horizontal towing force and vertical vibration force, easily causing local stress concentration and reducing structural reliability; Insufficient dynamic stability: Underwater equipment is easily affected by water flow impact and vibration during towing. Traditional single-lug or symmetrical double-lug structures have poor dynamic compensation capabilities for changes in the load center of gravity, easily causing component displacement or deformation; Complex installation and maintenance: Existing components mostly rely on bolts or welding for fixing, requiring high assembly precision and lacking modular design, resulting in low disassembly and assembly efficiency and difficulty in adapting to rapid deployment requirements; Weak shear resistance: Under the action of lateral shear force and torque, the lateral constraint of traditional structures is insufficient, easily leading to loosening or failure of connectors, affecting the overall structural strength.

[0003] Therefore, we propose an extender assembly for towing and extending underwater equipment to solve the above problems. Utility Model Content

[0004] In view of the problems existing in the prior art, this utility model discloses an extender assembly for towing and extending underwater equipment. The technical solution adopted includes a bracket A, a bracket B, and a main screw. The bracket A is composed of an outer plate assembly and a lug assembly. The outer plate assembly includes two outer vertical plates that are mirror-symmetrically distributed. The lug assembly includes two parallel load-bearing lugs. The two load-bearing lugs are welded and fixed at equal intervals in the vertical direction between the inner walls of the outer vertical plates. The outer walls of the load-bearing lugs and the inner walls of the outer vertical plates are connected by full-circumferential fillet welds to form a bidirectional force... At the transmission interface, the bracket B adopts a three-load-bearing lug layout based on the same spacing between the outer vertical plates. The three sets of load-bearing lugs are distributed equidistantly along the longitudinal direction between the outer vertical plates. Each load-bearing lug sidewall has a through lug hole. The bracket A and bracket B adopt a staggered assembly structure with a phase difference of 30°. Each lug hole forms a coaxial positioning channel. The main screw passes through the coaxial positioning channel, and its end is axially locked by a limit nut. The sidewalls of the two outer vertical plates in the same group of outer plate assemblies have corresponding through pin holes, and the pin holes of the two outer vertical plates are installed by a fixed pin.

[0005] As a preferred technical solution of this utility model, the thickness ratio of the load-bearing lug to the thickness of the outer vertical plate is 1:1.2, and the welding part is provided with a 45° chamfer transition structure.

[0006] As a preferred technical solution of this utility model, the inner side of the outer upright plate is provided with a positioning slot, and the end of the load-bearing lug is provided with a protruding structure that cooperates with the positioning slot.

[0007] As a preferred embodiment of this utility model, the side walls of the bracket A and the side walls of the bracket B are respectively provided with weight-reducing grooves.

[0008] The beneficial effects of this utility model are:

[0009] 1. Optimization of asymmetric force transmission path: The double lugs of bracket A and the triple lugs of bracket B are combined with a 30° phase difference staggered assembly to form a spatial staggered mechanical frame. The load is dispersed through the asymmetric force transmission path, which effectively avoids stress concentration and improves the fatigue resistance of the overall structure.

[0010] 2. Dual Redundant Load Transmission Chain: The main screw passes through the coaxial positioning channel and is pre-tightened by the limit nut, causing the lifting lugs of bracket A / B to undergo elastic deformation, forming a pre-stressed friction pair, which greatly improves the synchronous transmission efficiency of horizontal drag force and vertical vibration force, and at the same time realizes the dual redundancy insurance mechanism.

[0011] 3. Dynamic load compensation and enhanced stability: The longitudinal trapezoidal stress distribution design of the three lifting lugs of bracket B dynamically adjusts the load center of gravity through the intermediate load-bearing lifting lug, and combined with the bidirectional force transmission interface formed by the full-circumference fillet weld, significantly improves the component's resistance to displacement in complex water flow environments.

[0012] 4. Modular and rapid assembly: The combination design of the positioning slot and the raised structure simplifies the installation process of the outer upright plate and the load-bearing lifting lug; the lateral constraint mechanism of the pin hole and the fixing pin can achieve rapid disassembly and assembly while resisting shear force, reducing maintenance costs.

[0013] 5. Resistance to sudden stress changes and gradient transition: The load-bearing lugs and outer vertical plates adopt a 1:1.2 plate thickness ratio and a 45° chamfered weld design to form a gradient stress transition zone, which effectively alleviates local stress changes and extends the service life of the components. Attached Figure Description

[0014] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0015] Figure 1 This is a three-dimensional view of the structure of this utility model;

[0016] Figure 2 For reference regarding the structural usage of this utility model Figure 1 ;

[0017] Figure 3 For reference regarding the structural usage of this utility model Figure 2 ;

[0018] Figure 4 This utility model Figure 2 Exploded view of the structure;

[0019] Figure 5 This is a schematic diagram of the bracket B structure of this utility model;

[0020] Figure 6 This is a schematic diagram of the support structure A of this utility model.

[0021] In the diagram: 1. Bracket A, 2. Bracket B, 3. Outer plate assembly, 4. Lifting lug assembly, 5. Outer side upright plate, 6. Load-bearing lifting lug, 7. Lifting lug hole, 8. Main screw, 9. Limiting nut, 10. Weight reduction groove, 11. Pin hole, 12. Fixing pin. Detailed Implementation

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

[0023] like Figures 1 to 6As shown, this utility model discloses an extender assembly for towing and extending underwater equipment. The technical solution includes a bracket A1, a bracket B2, and a main screw 8. The bracket A1 consists of an outer plate assembly 3 and a lifting lug assembly 4. The outer plate assembly 3 includes two mirror-symmetrically distributed outer vertical plates 5. The lifting lug assembly 4 includes two parallel load-bearing lifting lugs 6. The two load-bearing lifting lugs 6 are welded and fixed at equal intervals along the vertical direction between the inner walls of the outer vertical plates 5. The outer walls of the load-bearing lifting lugs 6 and the inner walls of the outer vertical plates 5 are connected by full-circumferential fillet welds, forming a bidirectional force transmission interface. The bracket B2... Based on the same spacing of the outer vertical plates 5, a three-load-bearing lug 6 layout is adopted. The three sets of load-bearing lugs 6 are distributed equidistantly along the longitudinal direction between the outer vertical plates 5. Each load-bearing lug 6 has a through lug hole 7 on its side wall. The bracket A1 and the bracket B2 adopt a staggered assembly structure with a phase difference of 30°. Each lug hole 7 forms a coaxial positioning channel. The main screw 8 passes through the coaxial positioning channel, and its end is axially locked by the limit nut 9. The two outer vertical plates 5 in the same group of outer plate components 3 have corresponding through pin holes 11 on their side walls, and the pin holes 11 of the two outer vertical plates 5 are installed by a fixing pin 12.

[0024] By assembling brackets A1 and B2 with a 30° phase difference, a spatially interlaced mechanical frame is formed. The double-lug layout of bracket A1 and the triple-lug layout of bracket B2 constitute an asymmetrical force transmission path. After the main screw 8 is inserted into the coaxial positioning channel of the lug hole 7, a pulley for connecting external connectors is sleeved in the gap between the double lugs of bracket A1 and the triple lugs of bracket B2, forming a double redundant load transmission chain. At this time, the full-circumference fillet weld of bracket A1 transforms the contact surface between the load-bearing lug 6 and the outer vertical plate 5 into a bidirectional force transmission interface, realizing the horizontal drag force and vertical vibration force. The synchronous transmission of load is achieved by the three-lug layout of bracket B2 forming a trapezoidal stress distribution area in the longitudinal direction. The load center of gravity is dynamically compensated by adding a load-bearing lug 6 in the middle. When the external drag force is applied to the component, the main screw 8 acts as the central load shaft. The preload generated by the limit nut 9 causes the lug group of bracket A1 / B to undergo elastic deformation, forming a prestressed friction pair. The lateral constraint formed by the fixed pin 12 and the pin hole 11 is fixed. At the same time, a pulley for connecting the external component is sleeved at the position of the fixed pin 12 between the two outer vertical plates 5. While resisting the lateral shear force, part of the torque is converted into axial compressive stress.

[0025] As a preferred technical solution of this utility model, the thickness ratio of the load-bearing lug 6 to the thickness of the outer vertical plate 5 is 1:1.2, and the welding part is provided with a 45° chamfer transition structure. Through the 45° penetration depth design of the weld, the outer vertical plate 5 and the load-bearing lug 6 form a gradient stress transition zone, effectively avoiding stress abrupt change.

[0026] As a preferred technical solution of this utility model, the inner side of the outer upright plate 5 is provided with a positioning slot, and the end of the load-bearing lug 6 is provided with a protrusion structure that cooperates with the positioning slot. By adding the positioning slot and the corresponding protrusion structure, the installation stability of the outer upright plate 5 and the load-bearing lug 6 can be improved.

[0027] As a preferred technical solution of this utility model, the side wall of bracket A1 and the side wall of bracket B2 are respectively provided with weight reduction grooves 10.

[0028] The working principle of this utility model is as follows: By assembling bracket A1 and bracket B2 with a 30° phase difference, a spatially interlaced mechanical frame is formed. The double-lug layout of bracket A1 and the triple-lug layout of bracket B2 constitute an asymmetrical force transmission path. After the main screw 8 is inserted into the coaxial positioning channel of the lug hole 7, a pulley for connecting external connecting parts is sleeved in the gap between the double lugs of bracket A1 and the triple lugs of bracket B2, forming a double redundant load transmission chain. At this time, the full-circumference fillet weld of bracket A1 transforms the contact surface between the load-bearing lug 6 and the outer vertical plate 5 into a bidirectional force transmission interface, realizing the synchronous transmission of horizontal drag force and vertical vibration force. The triple-lug layout of bracket B2 forms a trapezoidal stress distribution area in the longitudinal direction, and the load-bearing capacity is increased in the middle. The lifting lug 6 achieves dynamic compensation of the load center of gravity. At the same time, by adding a slot and corresponding protrusion structure, the installation stability of the outer vertical plate 5 and the load-bearing lifting lug 6 can be improved. Through the 45° penetration design of the weld, the outer vertical plate 5 and the load-bearing lifting lug 6 form a gradient stress transition zone, effectively avoiding stress abrupt changes. When the external drag force is applied to the component, the main screw 8 acts as the central load main shaft. The preload generated by the limit nut 9 causes the lifting lug group of bracket A1 / B to undergo elastic deformation, forming a prestressed friction pair. The lateral constraint formed by the fixed pin 12 and the pin hole 11 is fixed. At the same time, a pulley for connecting the external component is sleeved at the position of the fixed pin 12 between the two outer vertical plates 5. While resisting the lateral shear force, part of the torque is converted into axial compressive stress.

[0029] The circuit connection involved in this utility model is a common method used by those skilled in the art, and technical inspiration can be obtained through a limited number of experiments. It belongs to the widely used prior art.

[0030] Components not described in detail in this article are existing technologies.

[0031] While the specific embodiments of this utility model have been described in detail above, this utility model is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of this utility model. Modifications or variations that do not involve creative labor are still within the protection scope of this utility model.

Claims

1. An extender assembly for towing and extending underwater equipment, comprising a bracket A (1), a bracket B (2), and a main screw (8), characterized in that, The bracket A (1) is composed of an outer plate assembly (3) and a lifting lug assembly (4). The outer plate assembly (3) includes two outer vertical plates (5) that are mirror-symmetrically distributed. The lifting lug assembly (4) includes two parallel load-bearing lifting lugs (6). The two load-bearing lifting lugs (6) are welded and fixed at equal intervals in the vertical direction between the inner walls of the outer vertical plates (5). The outer walls of the load-bearing lifting lugs (6) and the inner walls of the outer vertical plates (5) are connected by full-circumferential fillet welds to form a bidirectional force transmission interface. The bracket B (2) adopts a three-load-bearing lifting lug (6) layout based on the same spacing of the outer vertical plates (5). The three sets of load-bearing lifting lugs (6) are arranged in a three-way configuration. Ears (6) are distributed longitudinally at equal intervals between the outer vertical plates (5). Each load-bearing ear (6) has a through-hole (7) on its side wall. The bracket A (1) and bracket B (2) adopt a staggered assembly structure with a phase difference of 30°. Each ear hole (7) forms a coaxial positioning channel. The main screw (8) passes through the coaxial positioning channel, and its end is axially locked by a limiting nut (9). The two outer vertical plates (5) in the same group of outer plate components (3) have corresponding through-hole pin holes (11) on their side walls. The pin holes (11) of the two outer vertical plates (5) are fitted together by a fixed pin (12).

2. The extender assembly for towing and extending underwater equipment according to claim 1, characterized in that: The thickness of the load-bearing lug (6) is 1:1.2 to the thickness of the outer vertical plate (5), and the welding part is provided with a 45° chamfer transition structure.

3. The extender assembly for towing and extending underwater equipment according to claim 1, characterized in that: The outer side plate (5) has a positioning slot on its inner side, and the end of the load-bearing lug (6) has a protrusion structure that cooperates with the positioning slot.

4. The extender assembly for towing and extending underwater equipment according to claim 1, characterized in that: The side walls of the support A (1) and the support B (2) are respectively provided with weight reduction grooves (10).

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