CN111967101A - Method for designing deep sea pressure simulation device through mechanical pressurization - Google Patents

Method for designing deep sea pressure simulation device through mechanical pressurization Download PDF

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CN111967101A
CN111967101A CN202010736514.9A CN202010736514A CN111967101A CN 111967101 A CN111967101 A CN 111967101A CN 202010736514 A CN202010736514 A CN 202010736514A CN 111967101 A CN111967101 A CN 111967101A
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pressure
deep sea
base
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supporting part
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郑百林
江伟
张锴
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Tongji University
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    • G06—COMPUTING; CALCULATING OR COUNTING
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    • G06—COMPUTING; CALCULATING OR COUNTING
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    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • G06F30/23—Design optimisation, verification or simulation using finite element methods [FEM] or finite difference methods [FDM]
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    • G06F2111/06—Multi-objective optimisation, e.g. Pareto optimisation using simulated annealing [SA], ant colony algorithms or genetic algorithms [GA]
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    • G06F—ELECTRIC DIGITAL DATA PROCESSING
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    • G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces

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Abstract

The invention relates to a method for designing a deep sea pressure simulation device through mechanical pressurization, which comprises the following steps: (S-1) modeling: establishing a model of a deep sea pressure simulation device in simulation software ANSYS, wherein the model comprises a pressure-resistant device, a supporting part connected with the pressure-resistant device and a base connected with the pressure-resistant device; (S-2) stepwise pressurization and topology optimization: applying a simulated pressure to the pressure-resistant device through the supporting part on the model established in the step (S-1), and fixedly constraining the pressure-resistant device through the base; in the optimization process, analog pressure is applied to the pressure-resistant device, topology optimization is carried out on the pressure-resistant device, then the analog pressure is increased, topology optimization is carried out again, the analogy is repeated until the analog pressure is the design pressure, and the deep sea pressure simulation device is obtained through topology optimization. Compared with the prior art, the method has the advantages of being fast and convenient in design, high in accuracy and the like.

Description

Method for designing deep sea pressure simulation device through mechanical pressurization
Technical Field
The invention belongs to the field of design simulation for simulating deep sea pressure, and particularly relates to a method for designing a deep sea pressure simulation device through mechanical pressurization.
Background
The ocean accounts for about 71 percent of the surface area of the earth, and contains abundant seabed resources including petroleum, natural gas, various mineral substances and the like, the demand for resources is continuously increased due to the increase of population and economy, and the world inevitably focuses on the deep sea field in the future development in the face of gradual depletion of onshore and coastal resources, and the development towards the deep sea is an inevitable trend.
In the key technical field of equipment development, products in China still cannot meet the requirements, and key matching systems and equipment are basically monopolized abroad. Therefore, important special projects for guaranteeing the construction of the ocean forcing nation are researched and proposed as soon as possible, the basic, prospective and key technology research and development of the ocean field are strongly promoted, and the rapid promotion and development of the deep open sea capability become important.
The development of ocean resources is not independent of various mechanical test equipment, and at the present day of continuous breakthrough of diving depth, people already explore steps, continuous breakthrough of depth and step by step, and people already explore steps to the dark world of 7000m and even deeper. With the continuous and deep research on underwater operation, human beings put higher demands on the safety and reliability of deep-sea operation equipment. In the process of research and development of deep sea operation equipment, an essential step is to pass pressure tests with different indexes. When the depth of the seawater is increased by 10m, the corresponding pressure is increased by about 0.1MPa, the marine environment is complex, and the deeper the seawater, the harder the seawater is to test.
For a hydraulic system applied to a deepwater environment, the influence of water pressure on the system must be considered, otherwise, the hydraulic system cannot work normally, all tested elements are mostly installed on an experimental device and are sent to a preset ocean depth for testing in the current test method for seawater hydraulic elements, the test method is limited by various factors, such as the power supply problem, the weight of the experimental device and the like, the cost is high, the test is complex, the test safety is reduced due to various uncertain factors on the seabed, and the accuracy of the real performance evaluation of the seawater hydraulic elements is seriously influenced. For this reason, various simulation methods have been adopted by technologists, and conventionally, the hydraulic control element and the actuator are placed in a pressure container capable of bearing water pressure, which causes a series of problems of heavy system, complex structure, special dynamic seal and the like.
Disclosure of Invention
The invention aims to overcome the defects of poor accuracy and complex design process in the prior art and provide a method for designing a deep sea pressure simulation device by mechanical pressurization.
The purpose of the invention can be realized by the following technical scheme:
a method of designing a deep sea pressure simulation apparatus by mechanical pressurization, the method comprising the steps of:
(S-1) modeling: establishing a model of a deep sea pressure simulation device in simulation software ANSYS, wherein the model comprises a pressure-resistant device, a supporting part connected with the pressure-resistant device and a base connected with the pressure-resistant device;
(S-2) stepwise pressurization and topology optimization: applying a simulated pressure to the pressure-resistant device through the supporting part on the model established in the step (S-1), and fixedly constraining the pressure-resistant device through the base; in the optimization process, analog pressure is applied to the pressure-resistant device, topology optimization is carried out on the pressure-resistant device, then the analog pressure is increased, topology optimization is carried out again, the analogy is repeated until the analog pressure is the design pressure, and the deep sea pressure simulation device is obtained through topology optimization.
Further, in the step (S-1), the pressure resistant device includes a housing and an internal entity provided in the housing.
Further, the shell and the inner entity are both spherical, and the proportional relation between the diameter of the inner entity, the diameter of the inner cavity of the shell and the thickness of the shell is 250-270: 210-230: 15-25, preferably 260:220: 20.
Furthermore, the supporting part is of a truncated cone-shaped structure, and the large end of the truncated cone-shaped structure is attached to the surface of the pressure-resistant device.
Further, the ratio of the diameter of the large end of the truncated cone-shaped structure to the outer diameter of the shell is 150-170: 250 to 270, preferably 160: 260; the proportion relation of the diameter, the length and the diameter of the large end of the circular truncated cone-shaped structure is 40-50: 300-310: 155-165, preferably 45:305: 160.
Further, the base is cylindrical, and the diameter of the base is equal to the diameter of the large end of the support.
Furthermore, the number of the supporting parts is three, namely a first supporting part, a second supporting part and a third supporting part; the number of the bases is three, namely a first base, a second base and a third base; the second supporting part and the third supporting part are oppositely arranged, and the first supporting part is vertical to the second supporting part and the third supporting part; the first base is arranged opposite to the first supporting part, and the second base is arranged opposite to the third base.
Further, in the step (S-2), the initial simulated pressure is designed to be 0.05Mpa, and after each topology optimization is completed, the simulated pressure is increased by 0.1 to 0.2Mpa, preferably 0.1 Mpa.
Furthermore, during each topological optimization, the volume of the internal entity is reduced by adopting a finite element analysis method, then the shape structure of the internal entity is optimized to enable the integral rigidity of the pressure-resistant device to be the maximum value, and the stress difference of each point on the surface of the shell of the main body of the whole device is ensured to be less than or equal to 0.01MPa, so that the stress of each point on the surface of the shell of the main body of the whole device is ensured to be uniform.
Each reduction in volume of the internal body does not exceed 50% of the volume of the entire internal body.
Further, the material of the deep sea pressure simulation device is titanium alloy.
The design principle of the invention is as follows:
the optimization of the structure is completed by using a mature finite element analysis method and utilizing a topological optimization technology in software ANSYS, wherein the topological optimization is shape optimization and aims to seek the highest utilization rate of materials so as to enable an objective function (such as integral rigidity and natural frequency) to obtain the maximum or minimum value. The invention adopts an integral rigidity control method to ensure the maximum integral rigidity of the tested element and the uniformity of the stress of the tested element.
Compared with the prior art, the invention has the following advantages:
(1) the invention adopts simulation software ANSYS design, avoids a plurality of adverse factors such as temperature, salinity, dissolved oxygen, pH value, oxidation-reduction potential, biofouling, calcium ion deposition, surface flow velocity and the like related to hydrostatic pressure in an ocean test, makes the test simpler and safer, and reduces the test cost;
(2) the invention is modeled by a proper deep sea pressure simulation device, in the modeling process, the support adopts a small diameter at the pressure end, and the contact part with the spherical surface adopts a large diameter, so that the pressure can be uniformly transmitted; in addition, a plurality of supports and bases are adopted around the spherical surface, so that the consistency of the pressure around the spherical surface after optimization can be ensured, and if only one support is adopted, the uniformity of the pressure around the spherical surface is difficult to ensure no matter how the optimization is carried out in the actual calculation process;
(3) in the optimization process, firstly, the constraint that the volume reduction is not more than 50% is set, and after the shape of an internal entity is set and optimized, the overall rigidity is the maximum value; if the constraint of the volume reduction amount is not set in the topology optimization process, the volume may be too much or too little dug, the rigidity of the ball body after optimization is insufficient due to too much dug volume, the space in the cavity is insufficient due to too little dug volume, and in addition, if the rigidity is not constrained to be the maximum, the uniformity of the surface pressure of the dug ball body is difficult to ensure.
Drawings
FIG. 1 is a schematic diagram of a modeling structure of the present invention;
FIG. 2 is a front sectional view of a pressure-resistant apparatus according to the present invention;
FIG. 3 is a sectional view in a plan view of a pressure-resistant apparatus according to the present invention;
FIG. 4 is a side sectional view of a pressure-resistant apparatus according to the present invention;
FIG. 5 is an overall equivalent stress profile of the model of the present invention;
FIG. 6 is an equivalent stress distribution diagram of the deep sea pressure simulation apparatus of the present invention;
FIG. 7 is a diagram of the quasi-static pressure distribution of the cavity of the deep sea pressure simulator of the present invention;
FIG. 8 is a global pressure profile of the deep sea pressure simulation apparatus of the present invention;
in the figure, 1 is a pressure-resistant device, 2 is a support portion, 21 is a first support portion, 22 is a second support portion, 23 is a third support portion, 3 is a base, 31 is a first base, 32 is a second base, 33 is a third base, 4 is a solid structure, 41 is a concave structure, 42 is a support main body, 421 is an upper bottom surface, 422 is a lower bottom surface, 423 is a side surface, 43 is a support branch, 44 is a first through hole, 45 is a second through hole, and 5 is a housing.
Detailed Description
The present invention will be described in detail with reference to specific examples. The following examples will assist those skilled in the art in further understanding the invention, but are not intended to limit the invention in any way. It should be noted that variations and modifications can be made by persons skilled in the art without departing from the spirit of the invention. All falling within the scope of the present invention.
Examples
A method of designing a deep sea pressure simulation apparatus by mechanical pressurization, the method comprising the steps of:
(S-1) modeling: establishing a model of the deep sea pressure simulation device in simulation software ANSYS, wherein the model comprises a pressure-resistant device 1, a support part 2 connected with the pressure-resistant device 1 and a base 3 connected with the pressure-resistant device 1 as shown in figure 1; the pressure-resistant device 1 comprises a shell 5 and an internal entity arranged in the shell 5, wherein during modeling, the shell 5 and the internal entity are both spherical; the supporting part 2 is a circular truncated cone-shaped structure, the large end of the circular truncated cone-shaped structure is attached to the surface of the pressure-resistant device 1, the base 3 is cylindrical, and the diameter of the base 3 is equal to that of the large end of the supporting part 2; the structural dimensional parameters of each component are shown in table 1.
TABLE 1 structural parameters
Figure BDA0002605255510000041
As shown in fig. 1, the support portion 2 is provided with three, a first support portion 21, a second support portion 22 and a third support portion 23; the three bases 3 are respectively a first base 31, a second base 32 and a third base; the second support part 22 and the third support part 23 are oppositely arranged, and the first support part 21 is vertical to the second support part 22 and the third support part 23; the first base 31 is disposed opposite to the first support 21, and the second base 32 is disposed opposite to the third base.
(S-2) stepwise pressurization and topology optimization: applying a simulated pressure to the pressure-resistant device 1 through the support part 2 on the model established in the step (S-1), and fixedly constraining the pressure-resistant device 1 through the base 3; in the optimization process, applying simulation pressure to the pressure-resistant device 1, performing topology optimization on the pressure-resistant device 1, then increasing the simulation pressure, performing topology optimization again, and repeating until the simulation pressure is the design pressure, and performing topology optimization to obtain the deep sea pressure simulation device;
in the process of gradual pressurization, the initial simulated pressure is designed to be 0.05Mpa, and after each topological optimization is completed, the simulated pressure is increased by 0.1 Mpa.
During each topological optimization, a finite element analysis method is adopted to reduce the volume of an internal entity, then the shape structure of the internal entity is optimized to ensure that the integral rigidity of the pressure-resistant device 1 is the maximum value, and the stress difference of each point on the surface of the shell 5 of the main body of the whole device is ensured to be less than or equal to 0.01 MPa; each reduction in volume of the internal body does not exceed 50% of the volume of the entire internal body.
The structural schematic diagram of the finally optimized deep sea pressure simulator is shown in fig. 2, fig. 3 and fig. 4, wherein the deep color part is an internal solid structure 4 formed by residual materials of the solid part, and as can be seen from the figure, the volume of the internal solid part of the cavity is reduced by about 46 percent compared with the volume of the initial internal solid.
The optimized pressure-resistant device for deep sea exploration is essentially a pressure vessel, the structural schematic diagram of the deep sea pressure-resistant device is shown in fig. 2, fig. 3 and fig. 4, the solid structure 4 structure inside the optimized pressure-resistant device 1 comprises a supporting main body 42 fixedly connected with the inner wall of the shell at the periphery and supporting branches 43 connected with the supporting main body 42, the outer side surfaces 423 of the supporting branches 43 are fixed on the inner wall of the shell in a shape matching manner, the number of the supporting branches 43 is two, and the two supporting branches 43 are connected to two sides of the supporting main body 42 in a mirror symmetry manner. The supporting body 42 is a cylindrical structure, which includes an upper bottom 421 and a lower bottom 422 parallel to each other, and a side 423 disposed between the upper bottom 421 and the lower bottom 422, and the whole structure has a thick end and a thin middle, the edges of the upper bottom 421 and the lower bottom 422 are fixedly connected to the inner wall of the housing, and the middle side 423 is recessed toward the center of the sphere to form the recessed structure 41, and is not in contact with or fixed to the inner wall of the housing, i.e., the solid between the side 423 and the housing is also excavated. The support body 42 is provided with a first through hole 44 penetrating in the X direction, a second through hole 45 penetrating in the Y direction, the axial direction of the columnar structure is the Z direction, and the X direction, the Y direction, and the Z direction are perpendicular to each other. The first through hole 44 has a rectangular cross section. The second through hole 45 has a rectangular cross section. The distance between the upper bottom surface 421 and the lower bottom surface 422 is 0.3 times the diameter of the case. The intersection of the central axis of the cylindrical structure with the housing is the apex towards which the support branches 43 extend. The support branches 43 are thin shell structures with the inner side parallel to the outer side. The height of the support branches 43 is 0.6 times the radius of the housing in the axial direction of the cylindrical structure.
As can be seen from the figure, the volume of the inner solid part of the cavity is reduced by about 46% compared to the initial inner solid.
Further analyzing the overall and local stress distribution conditions of the device, the overall equivalent stress distribution of the whole model is shown in fig. 5, wherein the shell equivalent stress distribution of the pressure-resistant device 1 is shown in fig. 6, it can be seen that the shell surface equivalent stress distribution is uniform, and the individual few local stresses are larger because of the saint-wien effect in the mechanical algorithm, which does not affect the accuracy of the result. The overall static pressure distribution of the shell is shown in fig. 7, fig. 8 is a global pressure distribution diagram, and it can be seen that the pressure distribution around the cavity is uniform, so that the optimized cavity structure can completely meet the requirements of deep sea testing hydrostatic pressure environment, and can be used for testing deep sea pressure.
The foregoing description of specific embodiments of the present invention has been presented. It is to be understood that the present invention is not limited to the specific embodiments described above, and that various changes and modifications may be made by one skilled in the art within the scope of the appended claims without departing from the spirit of the invention.

Claims (10)

1. A method for designing a deep sea pressure simulation device by mechanical pressurization, the method comprising the steps of:
(S-1) modeling: establishing a model of the deep sea pressure simulation device in simulation software ANSYS, wherein the model comprises a pressure-resistant device (1), a supporting part (2) connected with the pressure-resistant device (1) and a base (3) connected with the pressure-resistant device (1);
(S-2) stepwise pressurization and topology optimization: on the model established in the step (S-1), applying simulated pressure to the pressure-resistant device (1) through the supporting part (2), and fixedly constraining the pressure-resistant device (1) through the base (3); in the optimization process, analog pressure is applied to the pressure-resistant device (1), topology optimization is carried out on the pressure-resistant device (1), then the analog pressure is increased, the topology optimization is carried out again, and the like until the analog pressure is the design pressure, and the deep sea pressure simulation device is obtained through the topology optimization.
2. The method for designing a deep sea pressure simulation device by mechanical pressurization according to claim 1, wherein in step (S-1), the pressure resistance device (1) comprises a housing and an internal entity disposed in the housing.
3. The method for designing the deep sea pressure simulation device through mechanical pressurization according to claim 2, wherein the shell and the internal entity are both spherical, and the ratio of the diameter of the internal entity, the diameter of the internal cavity of the shell and the thickness of the shell is 250-270: 210-230: 15 to 25.
4. The method for designing a deep sea pressure simulation device by mechanical pressing according to claim 2, wherein the supporting part (2) is a truncated cone structure and the large end of the truncated cone structure is attached to the surface of the pressure resistance device (1) in an abutting manner.
5. The method for designing a deep sea pressure simulation device through mechanical pressurization according to claim 4, wherein the ratio of the diameter of the large end of the truncated cone-shaped structure to the outer diameter of the shell is 150-170: 250 to 270 parts; the proportion relation of the diameter, the length and the diameter of the large end of the circular truncated cone-shaped structure is 40-50: 300-310: 155 to 165.
6. A method for designing a deep sea pressure simulation device by mechanical compression according to claim 4, characterized in that the base (3) is cylindrical and the diameter of the base (3) is equal to the diameter of the large end of the support (2).
7. A method for designing a deep sea pressure simulation device by mechanical pressurization according to claim 1, characterized in that the support part (2) is provided with three, a first support part (21), a second support part (22) and a third support part (23); the number of the bases (3) is three, namely a first base (31), a second base (32) and a third base; the second supporting part (22) and the third supporting part (23) are oppositely arranged, and the first supporting part (21) is vertical to the second supporting part (22) and the third supporting part (23); the first base (31) and the first supporting part (21) are arranged oppositely, and the second base (32) and the third base are arranged oppositely.
8. The method for designing a deep sea pressure simulation device by mechanical pressurization as claimed in claim 1, wherein the initial simulation pressure is designed to be 0.05Mpa in the step (S-2), and the simulation pressure is increased by 0.1 to 0.2Mpa after each topology optimization is completed.
9. The method for designing a deep sea pressure simulation device through mechanical pressurization as claimed in claim 1, wherein a finite element analysis method is adopted to reduce the volume of the internal entity during each topology optimization, and then the shape structure of the internal entity is optimized to make the overall rigidity of the pressure resistance device (1) be maximum, and the stress difference of each point on the surface of the shell of the whole device body is ensured to be less than or equal to 0.01 MPa.
10. The method of claim 9, wherein the volume of the internal body is reduced by no more than 50% of the entire volume of the internal body each time.
CN202010736514.9A 2020-07-28 2020-07-28 Method for designing deep sea pressure simulation device through mechanical pressurization Pending CN111967101A (en)

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