Cabin section structure capable of verifying deformation coordination capability of large buoyant raft vibration isolation system

Abstract

The invention discloses a cabin section structure capable of verifying the deformation coordination capability of a large buoyant raft vibration isolation system, which comprises a pressure-resistant hull shell plate and pressure-resistant hull ribs, and is characterized in that the sizes of the pressure-resistant hull shell plate and the pressure-resistant hull ribs are the same as the structural parameters of a real ship; the cabin section structure further comprises an end-thickened pressure-resistant shell ring, an oversized rib and a buoyant raft base. The end-thickened pressure-resistant shell rings are arranged at the two ends of the pressure-resistant hull shell plate. The oversized ribs are arranged at the two ends of the cabin section structure, and the distance between the two oversized ribs is equal to the distance between the two cabin walls of the underwater vehicle; the buoyant raft base is installed near the horizontal center line of the port and the starboard of the pressure-resistant hull shell plate. According to the cabin section structure, actual structure parameters of a real ship are adopted, a large external pressure test device is adopted for simulating the bearing condition which is consistent with the actual bearing of the real ship, real deformation can be accurately generated, and the most direct basis is provided for verifying the deformation compensation capacity of elastic components of the buoyant raft system under the limit depth.

Description

Technical Field

[0001] The invention relates to the technical field of hull structures, and in particular to a cabin structure for verifying the effectiveness of deformation coordination measures of a full-scale large-scale floating raft vibration isolation system. Background Art

[0002] The large floating raft vibration isolation system is an important means of mechanical noise control for underwater vehicles and is a system used at full depth by underwater vehicles. Multiple devices with hidden mechanical noise risks are integrated and installed on the floating raft. The equipment on the floating raft is connected to the pipeline on the pressure hull through a flexible pipe with a certain deformation compensation capability. The large floating raft is elastically connected to the hull base through the lower vibration isolator, and the base of the large floating raft is usually directly connected to the pressure hull rigidly. When the underwater vehicle dives into deep water, the hull structure will shrink and deform under pressure, while the floating raft structure itself has almost no deformation. Therefore, a relative deformation will form between the hull structure and the floating raft structure. This relative deformation may cause the performance of elastic components such as the lower vibration isolator and the flexible pipe to decrease or even be destroyed, thereby affecting the safety of the vibration isolation system and the pipelines connected to the vibration isolation system. At the same time, the non-uniform deformation of the hull structure is relatively complex. Therefore, it is necessary to comprehensively verify the deformation coordination ability of the large floating raft vibration isolation system under the real deformation conditions of the real load of the real-scale cabin structure, and verify the deformation compensation ability of the floating raft elastic components of the system at the extreme depth.

[0003] In addition, with the development of test support conditions, the large-scale external pressure test equipment was delivered and put into use as planned, providing the conditions for conducting external pressure tests on full-scale compartment models of underwater vehicles.

[0004] In view of this, the present invention proposes a cabin structure that can be used to verify the effectiveness of the deformation coordination measures of a full-scale large-scale floating raft vibration isolation system. By carrying out verification tests on this structure, the deformation compensation capability of the system's floating raft elastic components at extreme depths can be verified under real deformation conditions of real loads of the full-scale cabin structure. Summary of the invention

[0005] The main purpose of the present invention is to provide a cabin structure that can be used to verify the deformation coordination ability of a large floating raft vibration isolation system. The cabin structure meets the requirements of being tested in a large external pressure test device, and can assess the deformation compensation ability of the system's floating raft elastic components at extreme depths under real deformation conditions of real loads of a real-scale cabin structure.

[0006] The technical solution adopted by the present invention is: A cabin structure for verifying the deformation coordination capability of a large floating raft vibration isolation system comprises a pressure hull shell and pressure hull ribs, wherein the sizes of the pressure hull shell and the pressure hull ribs are the same as the structural parameters of an actual ship; the cabin structure also comprises an end thickened pressure shell ring, super-large ribs and a floating raft base; the end thickened pressure shell ring is arranged at both ends of the pressure hull shell; the super-large ribs are arranged at both ends of the cabin structure, and the distance between the two super-large ribs is the same as the distance between the two bulkheads of an underwater vehicle; the floating raft base is installed near the left and right horizontal center lines of the pressure hull shell.

[0007] In the above solution, the pressure hull plate is a cylindrical shell structure.

[0008] In the above scheme, the thickness of the end thickened pressure shell ring is 1.5-2 times the thickness of the pressure hull shell plate.

[0009] In the above solution, the length of the end thickened pressure-resistant shell ring is not less than 1 times the rib distance.

[0010] In the above scheme, the moment of inertia of the super-large rib is greater than 40 times the moment of inertia of the pressure hull rib.

[0011] In the above solution, a plurality of anti-tilt brackets are arranged around the super-large rib.

[0012] In the above solution, the super-large ribs are installed on the end thickened pressure-resistant shell ring.

[0013] In the above scheme, the raft base is installed below the horizontal center line of the pressure hull plate, and ensures that the bottom surface of the raft platform is flush with the horizontal center line.

[0014] In the above scheme, the panel of the floating raft base is firmly welded to the shell plate and ribs of the pressure hull through the patching plate.

[0015] In the above scheme, pads are welded on the panels of the floating raft base. After all pads are welded to the base panels, the pad surfaces are machined so that the deviation between the upper surface of the pads and the reference height is no more than 1 mm.

[0016] The beneficial effects produced by the present invention are: The cabin structure of the present invention has the same dimensions as the actual ship structure parameters for the pressure hull shell and the pressure hull ribs, which can ensure the simulation of the real deformation of the underwater vehicle; the thickened pressure shell rings at both ends of the pressure hull shell can avoid high stress concentration when the test heads are welded at both ends; the subdivision of the internal bulkhead is simulated by two super-large ribs, which can greatly simplify the bulkhead structure and reduce the construction workload; the raft base is installed below the left and right horizontal center lines of the pressure hull shell, and ensures that the bottom surface of the raft platform is flush with the horizontal center line, which can simulate the maximum radial deformation and maximize the deformation compensation capability. The cabin structure of the present invention adopts the actual structural parameters of the actual ship, and the load conditions are also simulated by a large external pressure test device to be consistent with the actual load of the actual ship, which can accurately produce real deformation, and provide the most direct basis for verifying the deformation compensation capability of elastic components of the raft system at extreme depths. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0018] Figure 1 is a schematic plan view of a cabin structure of a full-scale underwater vehicle in an embodiment of the present invention; Figure 2 yes Figure 1 A cross-sectional view of the raft platform area of ​​the compartment structure shown; Figure 3 yes Figure 1 A cross-sectional view of the super-large rib of the cabin structure is shown.

[0019] In the figure: 1. Thickened pressure hull ring at the end; 2. Extra-large ribs; 3. Anti-tilt brackets; 4. Pressure hull ribs; 5. Pressure hull shell plates; 6. Floating raft base. DETAILED DESCRIPTION

[0020] In order to make the purpose, technical solution and advantages of the present invention more clearly understood, the present invention is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not used to limit the present invention.

[0021] It should be noted that the illustrations provided in the embodiments of the present invention are only used to illustrate the basic concept of the present invention in a schematic manner. Therefore, the drawings only show components related to the present invention rather than being drawn according to the number, shape and size of components in actual implementation. In actual implementation, the type, quantity and proportion of each component may be changed arbitrarily, and the component layout type may also be more complicated.

[0022] In the present invention, it is also necessary to explain that, if the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. appear, the orientation or position relationship indicated is based on the orientation or position relationship shown in the drawings, which is only for the convenience of describing the present application and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present application. In addition, if the terms "first" and "second" appear, they are only used for description and distinction purposes, and cannot be understood as indicating or implying relative importance.

[0023] like Figure 1-3 As shown, a cabin structure for verifying the deformation coordination ability of a large floating raft vibration isolation system provided by an embodiment of the present invention includes a pressure hull shell plate 5 and a pressure hull rib 4. The dimensions of the pressure hull shell plate 5 and the pressure hull rib 4 are the same as the structural parameters of the actual ship. The same structural parameters as the actual ship can ensure the simulation of the real deformation of the underwater vehicle. The cabin structure also includes an end thickened pressure shell ring 1, an extra-large rib 2 and a floating raft base 6, wherein the end thickened pressure shell ring 1 is arranged at both ends of the pressure hull shell plate 5. The thickened pressure shell rings at both ends can avoid high stress concentration when the test heads are welded at both ends. The extra-large rib 2 is arranged at both ends of the cabin structure. The distance between the two extra-large ribs 2 is the same as the distance between the two bulkheads of the underwater vehicle. The extra-large rib 2 simulates the subdivision effect of the internal bulkhead. Since the bulkhead structure is too complicated and the construction amount is large, the use of the extra-large rib 2 in the present invention will greatly simplify the bulkhead structure, thereby reducing the construction amount. Since the extra-large ribs 2 are set at both ends, the floating raft platform structure needs to be placed in the cabin before the cabin shell rings are fully closed. Figure 2 As shown, the raft base 6 is installed below the horizontal center line of the left and right sides of the pressure hull plate 5, and ensures that the bottom surface of the raft platform is flush with the horizontal center line, which can simulate the maximum radial deformation and maximize the deformation compensation capability. The large-scale raft vibration isolation system is used normally under the actual maximum deformation condition, which provides the most direct basis for verifying the deformation compensation capability of the elastic components of the raft system at the extreme depth.

[0024] By installing a full-scale large-scale floating raft vibration isolation system in the cabin of the present invention, the deformation coordination ability of the large-scale floating raft vibration isolation system can be comprehensively verified, and the deformation compensation ability of related elastic components (including vibration isolators, flexible pipes, etc.) of the system at extreme depths can be verified.

[0025] In one embodiment of the present invention, the pressure hull plate 5 is a cylindrical shell structure.

[0026] In one embodiment of the present invention, the thickness of the end thickened pressure shell ring 1 is 1.5-2 times the thickness of the pressure hull plate 5 .

[0027] In one embodiment of the present invention, the length of the end thickened pressure shell ring 1 is not less than 1 times the rib distance.

[0028] In one embodiment of the present invention, the moment of inertia of the super-large rib 2 is greater than 40 times the moment of inertia of the pressure hull rib 4.

[0029] In one embodiment of the present invention, in order to ensure that the super-large rib 2 does not tilt, a plurality of anti-tilt brackets 3 are arranged in the circumference of the super-large rib 2 .

[0030] In one embodiment of the present invention, the super-large ribs 2 are installed on the end thickened pressure shell ring 1.

[0031] In one embodiment of the present invention, the panel of the floating raft base 6 is firmly welded to the pressure hull shell 5 and the pressure hull rib 4 through the patching plate.

[0032] In one embodiment of the present invention, a 20 mm pad is welded on the panel of the floating raft base 6. After all pads are welded to the base panel, the pad surface is machined so that the deviation between the upper surface of the pad and the reference height is no more than 1 mm. The pad is used to install the vibration isolator, and the floating raft platform is installed on the vibration isolator.

[0033] In one embodiment of the present invention, the pressure hull plate 5, the pressure hull rib 4, the end thickened pressure hull ring 1 and the super-large rib 2 are all made of high-strength steel used in the pressure hull of underwater vehicles, and are fixedly connected to each other by welding. The design is based on the actual ship structure size and the same materials to ensure the consistency of the model with the actual ship, ensuring that the deformation of the pressure hull under the actual deep water pressure condition can be most realistically simulated.

[0034] It should be noted that the feasibility of testing the full-scale cabin structure in a large-scale external pressure test device must be fully considered. An appropriate distance must be left between the periphery and the wall of the test device to ensure the installation of the transport track and trolley at the bottom of the external pressure test device, to ensure the limitation of the test device in the length direction, etc., to ensure the feasibility of the model test.

[0035] It should be pointed out that, according to the needs of implementation, the various steps / components described in this application can be split into more steps / components, and two or more steps / components or partial operations of steps / components can be combined into new steps / components to achieve the purpose of the present invention.

[0036] The order of execution of each step in the above embodiment does not mean the order of execution. The order of execution of each process should be determined by its function and internal logic, and should not constitute any limitation on the implementation process of the embodiment of the present application.

[0037] It should be understood that those skilled in the art can make improvements or changes based on the above description, and all these improvements and changes should fall within the scope of protection of the appended claims of the present invention.

Claims

1. A cabin structure for verifying the deformation coordination capability of a large floating raft vibration isolation system, comprising a pressure hull plate and a pressure hull rib, characterized in that: The dimensions of the pressure hull plate and the pressure hull ribs are the same as the actual ship structure parameters; the cabin structure also includes end thickened pressure hull rings, extra-large ribs and a raft base; the end thickened pressure hull rings are arranged at both ends of the pressure hull plate; the extra-large ribs are arranged at both ends of the cabin structure, and the distance between the two extra-large ribs is the same as the distance between the two bulkheads of the underwater vehicle; the raft base is installed near the left and right horizontal center lines of the pressure hull plate.

2. The cabin structure for verifying the deformation coordination capability of a large floating raft vibration isolation system according to claim 1 is characterized in that: The pressure hull shell is a cylindrical shell structure.

3. The cabin structure for verifying the deformation coordination capability of a large floating raft vibration isolation system according to claim 1 is characterized in that: The thickness of the end thickened pressure shell ring is 1.5-2 times the thickness of the pressure hull shell plate.

4. The cabin structure for verifying the deformation coordination capability of a large floating raft vibration isolation system according to claim 1 is characterized in that: The length of the end thickened pressure-resistant shell ring is not less than 1 times the rib distance.

5. The cabin structure for verifying the deformation coordination capability of a large floating raft vibration isolation system according to claim 1 is characterized in that: The moment of inertia of the super-large rib is greater than 40 times the moment of inertia of the pressure hull rib.

6. The cabin structure for verifying the deformation coordination capability of a large floating raft vibration isolation system according to claim 1 is characterized in that: A plurality of anti-tilt brackets are arranged around the super-large rib.

7. The cabin section structure for verifying the deformation coordination capability of a large floating raft vibration isolation system according to claim 1 is characterized in that: The extra-large ribs are mounted on the end thickened pressure-resistant shell ring.

8. The cabin structure for verifying the deformation coordination capability of a large floating raft vibration isolation system according to claim 1 is characterized in that: The floating raft base is installed below the horizontal center line of the pressure hull plate, and ensures that the bottom surface of the floating raft platform is flush with the horizontal center line.

9. The cabin structure for verifying the deformation coordination capability of a large floating raft vibration isolation system according to claim 1 is characterized in that: The panel of the floating raft base is firmly welded to the shell plate and ribs of the pressure hull through the patching plate.

10. The cabin structure for verifying the deformation coordination capability of a large floating raft vibration isolation system according to claim 9 is characterized in that: Pads are welded on the panels of the floating raft base. After all pads are welded to the base panels, the pad surfaces are machined so that the deviation between the upper surface of the pad and the reference height is no more than 1 mm.

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