Titanium alloy frame main structure for deep sea test

Abstract

The invention provides a titanium alloy frame main structure for a deep sea test, which comprises a stop transition ring, an upper frame and a lower frame which are sequentially fastened and connected from top to bottom to form a tower-shaped structure, a lifting position is arranged at the center of the top of the upper frame, and the upper frame and the lower frame are matched to form an accommodating space for mounting a main pressure-resistant cabin. The inner bottom side of the lower frame is provided with a main pressure-resistant cabin supporting seat of a spherical structure, and the peripheral side of the main pressure-resistant cabin supporting seat is provided with a plurality of equipment mounting seats used for mounting underwater equipment for testing. According to the invention, the transition ring, the upper frame and the lower frame of the tower-shaped structure are sequentially and fixedly connected from top to bottom, and the structural design is carried out by adopting a titanium alloy material and combining the adaptability of various working conditions, so that the problem that the stress condition of the main structure is complicated and changeable in different working scenes is solved; the effects that the main structure can adapt to various complex working conditions, and safe and reliable operation of the main structure is guaranteed are achieved.

Description

Technical Field

[0001] The present invention relates to the technical field of marine test devices, and in particular to a titanium alloy frame main structure for deep-sea testing. Background Art

[0002] The deep-sea environment, characterized by extreme high pressure, low temperatures, and severe corrosion, places extremely high demands on the structural materials of deep-sea exploration equipment. During deep-sea testing, the equipment must withstand the immense pressure of seawater while maintaining long-term stable performance to ensure smooth testing and accurate data acquisition.

[0003] An existing Chinese patent, CN105445174A, discloses a highly efficient, string-type deep-sea environmental testing device designed for medium- to long-term deep-sea environmental exposure testing at depths of 500 to 3000 meters. It is capable of conducting various corrosion and aging tests on metal materials, enabling more efficient and flexible deep-sea environmental testing. The device comprises a rope, a sample frame, a buoy, and a bottom anchor. The sample frame connects adjacent ropes in a straight line, one end of which is connected to the buoy and the other end to the bottom anchor via a release. The sample frame is made of titanium or a titanium alloy, and the test specimens are modularly mounted on the sample frame.

[0004] The existing main structure is subject to complex and variable stresses in various operating scenarios, such as deployment and recovery, deck securing, and single-side landing, making it difficult to ensure safe and reliable operation. Therefore, it is necessary to provide a structure designed to be adaptable to multiple operating conditions, thereby achieving high strength, high rigidity, and adaptability to multiple operating conditions for the main frame structure used in deep-sea testing. Summary of the Invention

[0005] In view of the defects in the prior art, the purpose of the present invention is to provide a titanium alloy frame main structure for deep-sea testing.

[0006] According to the present invention, a titanium alloy frame main structure for deep-sea testing is provided, which includes: a stabilizer transition ring, an upper frame, and a lower frame, which are fastened together in sequence from top to bottom to form a tower structure. A lifting position is provided at the top center of the upper frame, and the upper frame and the lower frame cooperate to form a accommodating space for installing a main pressure-resistant cabin. A main pressure-resistant cabin support seat with a spherical structure is provided on the inner bottom side of the lower frame. The main pressure-resistant cabin is fitted with the main pressure-resistant cabin support seat, and a plurality of equipment mounting seats for balancing the force transmission path are provided on the circumference of the main pressure-resistant cabin support seat.

[0007] Preferably, the stabilizer transition ring is arranged between the A-frame stabilizer and the upper frame, and the A-frame stabilizer passes through the stabilizer transition ring and is connected to the lifting position through the bearing head.

[0008] Preferably, the anti-oscillation transition ring includes two layers of circular rings with the same inner and outer diameters, the upper layer of the anti-oscillation transition ring has uniform circular holes, the lower layer of the anti-oscillation transition ring has uniform fan-shaped holes, and the lower layer of the anti-oscillation transition ring is fastened to the top of the upper frame.

[0009] Preferably, the upper frame includes an upper annular flange, a lower annular flange and four I-beam frame structures connecting the upper and lower layers. The outer diameter of the lower annular flange is larger than the outer diameter of the upper annular flange. A cross-shaped load-bearing beam is arranged at the center of the upper annular flange, and four lifting points are symmetrically arranged at the center of the cross-shaped load-bearing beam.

[0010] Preferably, the axis of the main pressure cabin coincides with the plumb line of the lifting position.

[0011] Preferably, the lower frame includes an upper open flange and a lower square flange, the disconnected portion of the open flange is connected by detachable plate bolts, and the top of the open flange is fastened to the lower annular flange by a connector.

[0012] Preferably, the equipment mounting seat includes: a battery box mounting seat, a power transformer mounting seat, a control transformer mounting seat, a power transformer mounting seat, an umbilical cord box mounting seat, multiple compensator mounting seats and multiple electric control cabin mounting seats. The battery box mounting seat and the power transformer mounting seat are arranged on two adjacent sides of the square flange, the power transformer mounting seat and the control transformer mounting seat are arranged on the side opposite to the power transformer mounting seat, and the umbilical cord box mounting seat is arranged on the side opposite to the battery box mounting seat.

[0013] Preferably, there are five compensator mounting seats, two of which are respectively arranged on the outside of the power transformer 2 mounting seat, two of which are respectively arranged on the outside of the power transformer 1 mounting seat and the control transformer 1 mounting seat, and one of which is arranged on the side of the umbilical cord box mounting seat close to the control transformer 1 mounting seat.

[0014] Preferably, the positive projection of the main pressure cabin support seat is cross-shaped, and four load-bearing beams corresponding to the main pressure cabin support seat are arranged on the outer side of the lower frame, and the load-bearing beams gradually extend outward from the top to the bottom of the lower frame. The three electric control cabin mounting seats are respectively arranged on the three load-bearing beams, and the three electric control cabin mounting seats are respectively arranged between the umbilical cord box mounting seat and the power transformer second mounting seat, between the battery box mounting seat and the power transformer second mounting seat, and between the battery box mounting seat and the power transformer first mounting seat.

[0015] Preferably, a protective net for resisting impact is provided at the bottom of the main pressure-resistant cabin support seat.

[0016] Compared with the prior art, the present invention has the following beneficial effects:

[0017] 1. The present invention forms a tower-shaped structure by sequentially fastening and connecting the stabilizer transition ring, upper frame and lower frame from top to bottom. The structure is designed with titanium alloy materials and combined with adaptability to multiple working conditions. The high strength, high rigidity and adaptability of the main structure of the deep-sea test frame to multiple working conditions are achieved, and the problem of complex and changeable stress conditions of the main structure in different working scenarios is solved, so that the main structure can adapt to a variety of complex working conditions and ensure its safe and reliable operation.

[0018] 2. The present invention takes into account the overall force transmission path of the frame and the installation space of the mounted equipment through the structural distribution of the equipment mounting seat, and seeks a reasonable balance between force transmission and installation space, so that the main structure can adapt to a variety of complex working conditions and ensure its safe and reliable operation.

[0019] 3. The present invention solves the problem of insufficient connection strength between the main structure and various functional components by adopting connection methods such as bolt fixing and combining strength verification with bolt verification standards, thereby ensuring that each component is firmly and stably installed on the main structure and can jointly withstand complex load conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Other features, objects and advantages of the present invention will become more apparent upon reading the detailed description of non-limiting embodiments with reference to the following drawings:

[0021] Figure 1 This is a schematic diagram of the main structure of the titanium alloy frame for deep-sea testing embodied in the present invention;

[0022] Figure 2 This is a schematic structural diagram of a transition ring of a stabilizer mainly embodied in the present invention;

[0023] Figure 3 This is a schematic structural diagram of the upper frame of the present invention;

[0024] Figure 4 This is a schematic structural diagram of the lower frame of the present invention;

[0025] Figure 5 This is a schematic structural diagram of the lower frame of the present invention;

[0026] Figure 6 This is a top view of the lower frame that mainly embodies the present invention.

[0027] As shown in the figure:

[0028] DETAILED DESCRIPTION

[0029] The present invention will be described in detail below with reference to specific embodiments. The following examples will help those skilled in the art to further understand the present invention, but are not intended to limit the present invention in any form. It should be noted that, for those skilled in the art, several changes and improvements can be made without departing from the scope of the present invention. These all fall within the scope of protection of the present invention.

[0030] like Figure 1-6 As shown, a titanium alloy frame main structure for deep-sea testing provided by the present invention includes: a stabilizer transition ring 1, an upper frame 2, and a lower frame 3, which are fastened together in sequence from top to bottom to form a tower structure. A lifting position 21 is provided at the top center of the upper frame 2. The upper frame 2 and the lower frame 3 cooperate to form a accommodating space for installing the main pressure cabin. A main pressure cabin support seat 31 with a spherical structure is provided on the inner bottom side of the lower frame 3. The main pressure cabin is fitted with the main pressure cabin support seat 31, and a plurality of equipment mounting seats for balancing the force transmission path are provided on the surrounding side of the main pressure cabin support seat 31.

[0031] Since the equipment has the requirement to touch the bottom, in order to increase the stability of the equipment after touching the bottom and take into account the rationality of the lifting load, the main structure is designed as a tower structure.

[0032] The stabilizer transition ring 1 is set between the A-frame stabilizer and the upper frame 2. The A-frame stabilizer passes through the stabilizer transition ring 1 and is connected to the lifting position 21 through the bearing head. The axis of the main pressure cabin coincides with the plumb line of the lifting position 21. The lifting position 21 is connected to the A-frame through the bearing head to realize the deployment and recovery of the main structure. The main pressure cabin is the core device of the equipment and is placed inside the main structure to ensure that its axis coincides with the plumb line of the lifting point. In order to facilitate the disassembly, assembly and maintenance of the main pressure cabin, the main pressure cabin is installed between the upper frame 2 and the lower frame 3, and a flange is used in the middle. In order to facilitate the overall pressure test of the main structure and the installation equipment in the pressure cylinder, the overall dimensions of the main structure are designed to be 2500×2500×3950mm, with a total weight of 718kg, and it is used to install functional components such as the pressure cabin, battery box, transformer, electric control cabin, umbilical box, etc.

[0033] The anti-oscillation transition ring 1 includes two layers of circular rings with the same inner and outer diameters. The upper layer of the anti-oscillation transition ring 1 has evenly opened circular holes, and the lower layer of the anti-oscillation transition ring 1 has evenly opened fan-shaped holes. The lower layer of the anti-oscillation transition ring 1 is firmly connected to the top of the upper frame 2.

[0034] The anti-sway transition ring 1 provides collision protection for the main structure through structural transition, ensuring stable docking and safe operation of the A-frame anti-sway. Bolts and nuts connect the anti-sway transition ring 1 to the upper frame 2. Its primary function is to transmit the balancing force required for equipment swinging in complex sea conditions to the anti-sway. The upper layer of the transition ring 1 is uniformly perforated with circular holes, while the lower layer is uniformly perforated with fan-shaped holes. These holes are designed to improve the convection environment of the local water flow near the frame.

[0035] The upper frame 2 includes an upper annular flange, a lower annular flange and four I-beam frame structures connecting the upper and lower layers. The outer diameter of the lower annular flange is larger than the outer diameter of the upper annular flange. A cross-shaped load-bearing beam is arranged at the center of the upper annular flange, and four lifting points are symmetrically arranged at the center of the cross-shaped load-bearing beam.

[0036] The upper frame 2 features an annular flange structure at the top and bottom. The upper flange primarily transmits force to the swing-stop transition ring 1, while the lower flange transfers force to the lower frame. Four I-beam-like skeletal structures, similar to the upper and lower flanges, transmit force between them and concentrate the force at the lower end to the bearing head connection point.

[0037] The lower frame 3 includes an upper open flange and a lower square flange. The disconnected portion of the open flange is connected by detachable plate bolts, and the top of the open flange is fastened to the lower annular flange by a connector.

[0038] The lower frame 3 is the main equipment installation platform and the cabin weight support platform. It must also take into account the equipment installation, disassembly, maintenance, and process testing. The upper side of the lower frame 3 adopts an "open" flange structure to facilitate installation after the entire cabin is integrated. The flange disconnected part is reinforced with a removable plate bolt connection. The lower flange of the lower frame 3 is square, on the one hand to facilitate the subsequent overall pressure resistance test of the equipment, and on the other hand to maximize the installation space and facilitate the installation of the electrical control cabin, transformer, etc. The surface of the two load-bearing beams on the inner side of the lower frame 3 is a spherical structure to increase the contact area with the pressure cabin and reduce local stress concentration in the pressure cabin.

[0039] The equipment mounting base includes: a battery box mounting base 32, a power transformer mounting base 33, a control transformer mounting base 34, a power transformer mounting base 35, an umbilical cord box mounting base 312, multiple compensator mounting bases and multiple electric control cabin mounting bases. The battery box mounting base 32 and the power transformer mounting base 35 are arranged on two adjacent sides of the square flange, the power transformer mounting base 33 and the control transformer mounting base 34 are arranged on the side opposite to the power transformer mounting base 35, and the umbilical cord box mounting base 312 is arranged on the side opposite to the battery box mounting base 32.

[0040] There are five compensator mounting seats, two of which are respectively arranged on the outside of the power transformer second mounting seat 35, two compensator mounting seats are respectively arranged on the outside of the power transformer first mounting seat 33 and the control transformer first mounting seat 34, and one compensator mounting seat is arranged on the side of the umbilical cord box mounting seat 312 close to the control transformer first mounting seat 34.

[0041] The positive projection of the main pressure cabin support seat 31 is cross-shaped. Four load-bearing beams corresponding to the main pressure cabin support seat 31 are arranged on the outer side of the lower frame 3. The load-bearing beams gradually extend outward from the top to the bottom of the lower frame 3. The three electric control cabin mounting seats are respectively arranged on the three load-bearing beams. The three electric control cabin mounting seats are respectively arranged between the umbilical cord box mounting seat 312 and the power transformer second mounting seat 35, between the battery box mounting seat 32 and the power transformer second mounting seat 35, and between the battery box mounting seat 32 and the power transformer first mounting seat 33.

[0042] A protective net 311 for resisting impact is provided at the bottom of the main pressure cabin support seat 31.

[0043] This application is further elaborated through the following data. The spherical main pressure cabin support seat 31 supports the 4294kg main pressure cabin. The battery box mounting seat 32 installs a 50kg battery box. The power transformer 1 mounting seat 33 installs the 141.5kg power transformer 1, the control transformer 1 mounting seat 34 installs the 97.39kg control transformer, and the power transformer 2 mounting seat 35 installs the 141.5kg power transformer 2. The compensator mounting seats 36-310 are respectively installed with 5 compensators with a single weight of 5kg. The protective net 311 provides impact protection for the equipment and connecting cables installed on the main structure. The umbilical cord box mounting seat 312 is installed with a 43kg umbilical cord box. The electric control cabin mounting seats 313-315 are respectively installed with 3 electric control cabins with a single weight of 93.81kg. The structural distribution of the equipment mounting seat takes into account both the overall force transmission path of the frame and the installation space of the carried equipment, and seeks a reasonable balance between force transmission and installation space. The remaining scattered weight is 132.5kg. The device and the mounting base are fixed with bolts.

[0044] The primary structure is the primary load-bearing structure for system deployment, retrieval, and deck securing. It must possess sufficient strength and rigidity to meet operational requirements. The primary structure design requires strength analysis and assessment, considering three load conditions: top lifting, bottom support, and single-side landing.

[0045] The main structure adopts TC4 titanium alloy, whose yield strength σs=825Mpa.

[0046] A finite element calculation model was established: the main load-bearing frame structural members, such as the main structure plates (upper frame 2, lower frame 3, frame flange connection plates and various brackets, etc.), were simulated using 2-D shell elements; the main pressure cabin support seat 31 was simulated using 3-D solid elements; the bolted connection was simulated using RBE2+BAR+RBE2 elements; the welded parts were simulated using a grid common node method; the equipment counterweight was simulated using RBE3+MASS, and the position of MASS was based on the actual center of mass of the equipment; the scattered mass simulation without considering the center of mass position was uniformly distributed on its load-bearing surface, and the overall mass was divided by the number of nodes involved and evenly distributed on each node.

[0047] Top-lift load conditions: According to Lloyds' Register of Shipping's "Lloyds Code for Lifting Appliances in a Marine Environment," when operating in Beaufort Scale 5 sea conditions, the operating factor is 1.2 and the dynamic load factor is 2.25. The load safety factor is: Load safety factor = operating factor × dynamic load factor = 1.2 × 2.25 = 2.7. In the finite element model, an inertial acceleration of 2.7g (downward) was applied to the entire model. The lifting position was constrained to 6 degrees of freedom (SPC12345). The weight of the main pressure tank, battery box, transformer, and other working equipment was applied to the main structure according to the weight center of gravity table.

[0048] Bottom support load conditions: According to the China Classification Society's "Diving Systems and Submersibles Classification Rules", submersibles placed on ships should be designed to withstand the combined forces of the following two conditions due to the movement of the ship:

[0049] (1) The acceleration perpendicular to the deck is ±1.0g

[0050] The acceleration in the fore-aft direction parallel to the deck is: ±0.5g

[0051] (2) The acceleration perpendicular to the deck is ±1.0g

[0052] Transverse acceleration parallel to the deck: ±0.5g

[0053] The bottom surface is constrained in the Z vertical direction. Four pull rings are located on the central flange of the frame to constrain translation in the X, Y, and Z directions. The load is the weight of the equipment, while also taking into account the combined acceleration loads mentioned above.

[0054] Single-side touchdown load condition: Considering the possibility of a single-side touchdown during the recovery and lowering of the entire system onto the shipboard platform, a strength condition verification was conducted for this special scenario to examine whether the strength meets the performance requirements when the single-side touchdown state is in place. In the finite element model for the single-side touchdown condition, an inertial acceleration of 1g (downward) was applied to the entire model. With the main structure tilted 15°, SPC123456 degrees of freedom were constrained at the lifting position and the single-side touchdown position.

[0055] Strength criterion: According to the China Classification Society's "Diving Systems and Submersibles Classification Rules" and the UK Lloyds Register's "Lloyds code for Lifting Appliances in a Marine Environment", the material safety factor is taken as 1.5, then the allowable stress of titanium alloy material is: allowable stress [σ] = σs / safety factor = 825 / 1.5 = 550MPa.

[0056] The allowable stress standards for different stress states are shown in the following table.

[0057] Stress state Allowable stress value tensile stress 1.0[σ]=550 compressive stress 1.0[σ]=550 shear stress 0.58[σ]=319 Considerable stress 1.1[σ]=605

[0058] Table 1 Allowable stress values ​​of components (MPa)

[0059] According to 2.23.5 of the Lloyds Code for Lifting Appliances in a Marine Environment, the bolt verification standards are shown in the table below. Bolt material: A40-80, yield strength: 600 MPa.

[0060] Stress state Allowable stress value of bolts tensile stress <![CDATA[0.4σ y =240]]> shear stress <![CDATA[0.38σ y =228]]>

[0061] Table 2 Allowable stress values ​​of bolts (MPa)

[0062] Finite element analysis verification results:

[0063] Under the top lifting load condition, the main structure and bolts meet the strength requirements. The verification results are shown in the table below.

[0064]

[0065] Table 3 Structural strength verification under top lifting load conditions Under bottom supporting load conditions, the main structure and bolts meet the strength requirements. The verification results are shown in the table below.

[0066]

[0067]

[0068]

[0069] Table 4 Structural strength verification under bottom support load conditions Under the single-side ground load condition, the main structure and bolts meet the strength requirements. The verification results are shown in the table below.

[0070]

[0071] Table 5 Structural strength verification for single-side ground load conditions

[0072] In summary, under the top lifting, bottom support and unilateral ground load conditions, the stress results all meet the strength performance requirements.

[0073] This application uses titanium alloy materials and combines a structure with a variety of working condition adaptability designs to achieve high strength, high rigidity, and adaptability to multiple working conditions for the main structure of the deep-sea test frame. This application solves the problem of complex and changeable stress conditions of the main structure in different working scenarios (such as deployment and recovery, deck fastening, unilateral landing, etc.) by adopting a variety of working condition adaptability designs (such as top lifting load condition design, bottom support load condition design, unilateral landing load condition design, etc.), achieving the effect of enabling the main structure to adapt to a variety of complex working conditions and ensuring its safe and reliable operation.

[0074] This application solves the problem of insufficient connection strength between the main structure and various functional components by adopting connection methods such as bolt fixing and combining strength verification with bolt verification standards, thereby ensuring that each component is firmly and stably installed on the main structure and can jointly withstand complex load conditions.

[0075] In the description of this application, it should be understood that the terms "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do 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 this application.

[0076] The above describes specific embodiments of the present invention. It should be understood that the present invention is not limited to the specific embodiments described above, and those skilled in the art may make various changes or modifications within the scope of the claims, which do not affect the essence of the present invention. The embodiments of this application and the features in the embodiments may be combined with each other in any manner unless there is a conflict.

Claims

1. A titanium alloy frame main structure for deep-sea testing, characterized in that: The invention comprises: a stabilizer transition ring (1), an upper frame (2), and a lower frame (3) which are fastened and connected in sequence from top to bottom to form a tower structure; a lifting position (21) is provided at the top center of the upper frame (2); the upper frame (2) and the lower frame (3) cooperate to form a receiving space for installing a main pressure-resistant cabin; a main pressure-resistant cabin support seat (31) with a spherical structure is provided on the inner bottom side of the lower frame (3); the main pressure-resistant cabin is fitted with the main pressure-resistant cabin support seat (31); and a plurality of equipment mounting seats for installing underwater test equipment are provided on the peripheral side of the main pressure-resistant cabin support seat (31).

2. The titanium alloy frame main structure for deep sea testing according to claim 1, characterized in that: The stabilizer transition ring (1) is arranged between the A-frame stabilizer and the upper frame (2); the A-frame stabilizer passes through the stabilizer transition ring (1) and is connected to the lifting position (21) via a bearing head.

3. The titanium alloy frame main structure for deep sea testing according to claim 1, characterized in that: The anti-oscillation transition ring (1) comprises two layers of circular rings with the same inner and outer diameters, the upper layer of the anti-oscillation transition ring (1) has uniform circular holes, the lower layer of the anti-oscillation transition ring (1) has uniform fan-shaped holes, and the lower layer of the anti-oscillation transition ring (1) is firmly connected to the top of the upper frame (2).

4. The titanium alloy frame main structure for deep sea testing according to claim 1, characterized in that: The upper frame (2) comprises an upper annular flange, a lower annular flange and four I-beam skeleton structures connecting the upper and lower layers, the outer diameter of the lower annular flange is larger than the outer diameter of the upper annular flange, a cross-shaped load-bearing beam is arranged at the center of the upper annular flange, and four lifting points are symmetrically arranged at the center of the cross-shaped load-bearing beam.

5. The titanium alloy frame main structure for deep sea testing according to claim 1, characterized in that: The axis of the main pressure cabin coincides with the plumb line of the lifting position (21).

6. The titanium alloy frame main structure for deep sea testing according to claim 1, characterized in that: The lower frame (3) comprises an upper open flange and a lower square flange, the disconnected portion of the open flange is connected by detachable plate bolts, and the top of the open flange is fastened to the lower annular flange by a connector.

7. The titanium alloy frame main structure for deep sea testing according to claim 6, characterized in that: The equipment mounting seat comprises: a battery box mounting seat (32), a power transformer mounting seat (33), a control transformer mounting seat (34), a power transformer mounting seat (35), an umbilical box mounting seat (312), a plurality of compensator mounting seats and a plurality of electric control cabin mounting seats, wherein the battery box mounting seat (32) and the power transformer mounting seat (35) are arranged on two adjacent sides of the square flange, the power transformer mounting seat (33) and the control transformer mounting seat (34) are arranged on a side opposite to the power transformer mounting seat (35), and the umbilical box mounting seat (312) is arranged on a side opposite to the battery box mounting seat (32).

8. The titanium alloy frame main structure for deep sea testing according to claim 7, characterized in that: There are five compensator mounting seats, two of which are respectively arranged on the outside of the second power transformer mounting seat (35), two of which are respectively arranged on the outside of the first power transformer mounting seat (33) and the first control transformer mounting seat (34), and one of which is arranged on the side of the umbilical box mounting seat (312) close to the first control transformer mounting seat (34).

9. The titanium alloy frame main structure for deep sea testing according to claim 7, characterized in that: The positive projection of the main pressure cabin support seat (31) is cross-shaped, and four bearing beams corresponding to the main pressure cabin support seat (31) are arranged on the outer side of the lower frame (3), and the bearing beams gradually extend outward from the top to the bottom of the lower frame (3), and the three electric control cabin mounting seats are respectively arranged on the three bearing beams, and the three electric control cabin mounting seats are respectively arranged between the umbilical box mounting seat (312) and the power transformer second mounting seat (35), between the battery box mounting seat (32) and the power transformer second mounting seat (35), and between the battery box mounting seat (32) and the power transformer first mounting seat (33).

10. The titanium alloy frame main structure for deep sea testing according to claim 1, characterized in that: The bottom of the main pressure-resistant cabin support seat (31) is provided with a protective net (311) for resisting impact.

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