CN109949879A - A kind of submarine navigation device pressure hull self-strengthening method - Google Patents
A kind of submarine navigation device pressure hull self-strengthening method Download PDFInfo
- Publication number
- CN109949879A CN109949879A CN201910204443.5A CN201910204443A CN109949879A CN 109949879 A CN109949879 A CN 109949879A CN 201910204443 A CN201910204443 A CN 201910204443A CN 109949879 A CN109949879 A CN 109949879A
- Authority
- CN
- China
- Prior art keywords
- stress
- cylinder
- formula
- self
- external pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Landscapes
- Working Measures On Existing Buildindgs (AREA)
- Pressure Vessels And Lids Thereof (AREA)
Abstract
A kind of submarine navigation device pressure hull self-strengthening method, the present invention relates to oceanographic equipment technical fields；Its operating procedure is as follows: the selection of material model；Traditional cylinder pressure hull structure cylindrical band rib structure, cylinder are analyzed without the intensity of rib structure；Its residual stress is lost after external pressure in the regularity of distribution in wall thickness direction in the cylinder that elastic-plastic deformation occurs according to, to the definition of residual stress, deriving in the mechanics of materials；Derive the relationship between the magnitude of interference of formed punch and elastic-plastic interface radius；Obtain most preferably surrendering radius, be in full yield situation when bearing external pressure value and cylinder, bearing capacity theory lifting values after derivation Self-enhancement treatment, under the action of external pressure, on cylindrical wall at the radius caused by axial stress.So that bearing capacity of submarine navigation device on the basis of original structure is greatly improved, stability is good, and practicability is stronger.
Description
Technical field
The present invention relates to oceanographic equipment technical fields, and in particular to a kind of submarine navigation device pressure hull self-strengthening method.
Background technique
In following development, ocean certainly will will become the Main way of China's development.To the exploitations of marine resources with
Using relevant technical support is needed, such as the pressure-resistant technology of the Detection Techniques at deep-sea, control technology and big depth, deep sea diving
The position that can be reached has been largely fixed institute can investigative range.And current stage, China's maximum bathyscaph submerged depth
Making the country prosperous with oceans such as the U.S., there are also the gaps of a bit.For technically, there is still a need for right in material and two aspects of structure in China
Big depth pressure hull technology is promoted.
It is titanium alloy material and composite material such as carbon fiber that the strength of materials is higher at present, both materials all can be big
Amplitude mitigates the weight of pressure hull while promoting pressure hull bearing capacity.I.e. specific gravity is lighter, but specific strength is higher, thus
The mobility and reserve buoyancy of aircraft are improved, with the more equipment of Portable belt and apparatus for work.But titanium alloy and multiple
Condensation material at present for aluminium alloy there are the problem of it is mainly expensive, formability is bad, and welding performance is poor.This
The cost of manufacture for allowing for submersible is significantly promoted, therefore in the case where current titanium alloy does not obtain large-area applications,
It needs further to promote traditional aluminum alloy materials performance.Harmful residual stress generates the curved of such as metal material
The inhomogeneous deformation and phase transformation that are generated during bent, cutting, welding and heat treatment etc. and stroke, this residual stress due to
It is unevenly distributed, the nature of industrial production and material can be had adverse effect on.But for occurring uniformly due to material
Elastic-plastic deformation and the residual stress that generates, not only can use the bearing capacity of raising internal pressure or external pressure vessel,
And will not be because of natrual ageing the reason of, slowly disappears.
At present for the application study that most of self-reinforcing technology is in terms of internal pressure receiving, self-reinforcing technology is being held
Application in terms of by external pressure, presently relevant research are less.For self-reinforcing technology, aircraft pressure hull bears external pressure under water
The application of aspect, has no correlative study both at home and abroad.How to realize that aircraft pressure hull is born under water for self-strengthening method
Research application in terms of external pressure is key point.
Summary of the invention
In view of the defects and deficiencies of the prior art, the present invention intends to provide a kind of structure is simple, design rationally, make
With convenient submarine navigation device pressure hull self-strengthening method, so that bearing capacity of submarine navigation device on the basis of original structure
It is greatly improved, stability is good, and practicability is stronger.
To achieve the above object, the technical solution adopted by the present invention is that: its operating procedure is as follows:
1, the selection of material model:
Material model is simplified first before autofrettage model foundation, it otherwise will be under cylinder elastic-plastic behavior
The solution of ess-strain bring very big difficulty；The method being often used is the modelling of deformable body, and exponential hardening model is contained
The material type of lid is most, most accurate for some materials performance fitted, but its theoretical model is complex, ideal elastic-plastic
Material material biggish for hardenability can be very good the relationship between reflection stress and strain substantially, and to hardenability
Although lesser material cannot accurately reflect the truth of material deformation very much, by related correction factor to calculated result
It is modified and is just sufficient for being actually needed, and reduce the difficulty of calculating；Aluminum alloy materials are selected, it is smaller to belong to hardenability
Material, analyzed using ideal elastoplastic model；
2, traditional cylinder pressure hull structure cylindrical band rib structure, cylinder are analyzed without the intensity of rib structure, in turn
Cylindrical structure is obtained on the process shell wall thickness direction for bearing internal pressure and external pressure according to the elastic-plastic strain equation of cylindrical structure
Stress distribution law and occur elastic and plastic deformation process in required external pressure；
3, according to, to the definition of residual stress, derived in the mechanics of materials occur elastic-plastic deformation cylinder lose outside
The regularity of distribution of its residual stress in wall thickness direction after pressure；
4, using above-mentioned steps 2 and step 3 theory analysis as a result, by elastic-plastic interface radius and hydraulic self-reinforcing
Journey processing pressure applies in mechanical self-reinforcing mode, derives between the magnitude of interference of formed punch and elastic-plastic interface radius
Relationship obtains the bullet of hydraulic self-reinforcing process according to the relationship between the stress and strain of elastic-perfectly plastic material in loading procedure
Plastic stress Strain Distribution；
When cylinder bears external pressure, the relationship between radial displacement u and elastoplasticity radius and external pressure is as follows:
E is the elasticity modulus of cylinder in (formula 1), and μ is the Poisson's ratio of cylinder, and k is the diameter ratio b/a of cylinder；
When formed punch bears external pressure, for formed punch, since its material is harder, and yield strength is very high, thus in punching course
Its generation flexible deformation is available according to the relevant knowledge in Elasticity without being plastically deformed in the middle:
U in (formula 2)1For the elastic displacement of formed punch, E1For the elasticity modulus of formed punch, μ1For the Poisson's ratio of formed punch, a1For
Formed punch minimum diameter (i.e. with the internal diameter of the part of cylinder interference), b1For the outer diameter of formed punch, k1For the diameter ratio of formed punch；
Relational expression between simultaneous (formula 1) (formula 2) available magnitude of interference:
u1+u-b+a1=0 (formula 3)
5, it obtains most preferably surrendering radius, the stress value as caused by inner surface is all larger than the stress at other positions of cylinder
Value, as receiving external pressure value p2And cylinder is in full yield situation, i.e. rpHave when=b:
P in formulajRequired limit external pressure value when occurring to be plastically deformed entirely for cylinder；
At this point, the equivalent stress of the residual stress at inner surface are as follows:
K in formulaj=rp/ a, k=b/a；
Above formula, which is unfolded, according to Taylor's formula to obtain:
This has formula (formula 7):
So as to obtain formula (formula 8):
So on the inner surface of cylinder, the equivalent stress of residual stress is negative value, in the expression formula of equivalent stress,
When cylinder reaches full yield situation, kj=k, bringing into formula can obtain:
Due toWhen, surrender completely will occur for material, it is therefore desirable toIt is available:
K≤2.218457489... is solved, it is possible thereby to know, as k≤2.218457489..., cylinder will not occur
The phenomenon that reverse yielding, and as k > 2.218457489..., cylinder can there is a phenomenon where reverse yieldings；
It enablesIt can be obtained when the relationship between the best plastic radius and diameter ratio of k > 2.218457489..., such as
Shown in lower:
6, bearing capacity theory lifting values after derivation Self-enhancement treatment, in external pressure p'2Under the action of, in radius on cylindrical wall
Axial stress caused by r are as follows:
Radial stress are as follows:
Circumference stress are as follows:
It is available according to meter Sai Si Stress calculation formula, in external pressure p2Under effect, generated stress are as follows:
In view of the influence of residual stress, produced by residual stress with the external pressure born after carrying out Self-enhancement treatment
Raw total meter Sai Si stress are as follows:
In formula:WithRespectively remaining radial stress and remaining circumference stress；
Since autofrettaged cylinder is during bearing external pressure, maximum stress point not necessarily will appear on an internal surface,
The residual tension of inner surface can be overlapped with compression caused by external pressure can balance out a part of stress value, and outer surface
Residual compressive stress can add up with compression caused by external pressure, cause the promotion of outer surface stress, thus calculate from
When enhancing cylinder bearing capacity, need respectively to calculate the stress of elastic region and plastic zone；
Plastic zone:
The σ when plastic zone is surrendereds=σs, that is:
It solves:
Available by derivative concept, this formula is in rpMaximum value is obtained when=b, that is to say, that for diameter ratio less than 2.2184
Cylinder, when during Self-enhancement treatment occur all surrender when, generated residual stress can improve to the greatest extent
The bearing capacity of pressure hull, the also referred to as best surrender radius of this surrender radius, it is contemplated that in pressure hull process
Safety and use environment requirement, cannot generally reach 100% full surrender, and be controlled at 50%~70%；
Elastic region:
It enablesI.e. obtained in the best plastic zone radius aboveHolding after available Self-enhancement treatment
Pressure energy power becomes:
Due in the cylinder without Self-enhancement treatment,When just have occurred that yield phenomenon,
And can see after Self-enhancement treatment, bearing capacity improves twice.
After above-mentioned steps, the invention has the following beneficial effects: a kind of submarine navigation device pressure hull of the present invention is certainly
Enhancement Method, so that bearing capacity of submarine navigation device on the basis of original structure is greatly improved, stability is good, real
The advantages that stronger with property, the present invention has structure simple, is arranged rationally, low manufacture cost.
Detailed description of the invention
In order to more clearly explain the embodiment of the invention or the technical proposal in the existing technology, to embodiment or will show below
There is attached drawing needed in technical description to be briefly described, it should be apparent that, the accompanying drawings in the following description is only this
Some embodiments of invention for those of ordinary skill in the art without creative efforts, can be with
It obtains other drawings based on these drawings.
Radial direction residual stress is in the radial direction when Fig. 1 is hydraulic self-reinforcing difference yield strength in specific embodiment
Distribution map.
Circumferential direction residual stress is in the radial direction when Fig. 2 is hydraulic self-reinforcing difference yield strength in specific embodiment
Distribution map.
Fig. 3 is the cylinder pressure hull radial direction residual stress comparison of hydraulic self-reinforcing different wall thickness in specific embodiment
Figure.
Fig. 4 is the cylinder pressure hull circumferential direction residual stress comparison of hydraulic self-reinforcing different wall thickness in specific embodiment
Figure.
Fig. 5 is cylinder pressure hull radial direction residual stress comparison of the hydraulic self-reinforcing difference diameter than under in specific embodiment
Figure.
Fig. 6 is cylinder pressure hull circumferential direction residual stress comparison of the hydraulic self-reinforcing difference diameter than under in specific embodiment
Figure.
Fig. 7 is that the cylinder pressure hull in specific embodiment under hydraulic self-reinforcing difference Self-enhancement treatment pressure is radially residual
Residue stress comparison diagram.
Fig. 8 is that the cylinder pressure hull circumferential direction in specific embodiment under hydraulic self-reinforcing difference Self-enhancement treatment pressure is residual
Residue stress comparison diagram.
Fig. 9 is the relational graph in specific embodiment between yield strength and radial residual stress maxima and minima.
Figure 10 is the relational graph in specific embodiment between yield strength and circumferential residual stress maxima and minima.
Figure 11 is the relational graph in specific embodiment between wall thickness and radial residual stress maxima and minima.
Figure 12 is the relational graph in specific embodiment between wall thickness and circumferential residual stress maxima and minima.
Specific embodiment
The present invention will be further described below with reference to the drawings.
Referring to as shown in Fig. 1-Figure 12, present embodiment the technical solution adopted is that: it is resistance in present embodiment
The internal-and external diameter of pressure shell body is taken as 284mm and 324mm respectively, and the radius of yield strength 100-700Mpa, elastic-plastic interface are equal
For 152mm, it is 100Mpa, 300Mpa, 500Mpa, 700Mpa that yield strength is chosen from the result of analysis.Choosing wall thickness is
10mm, 20mm, 30mm, 40mm's analyze；Its Detailed operating procedures is as follows:
1, the foundation of hydraulic self-reinforcing simulation model, by ANSYS and MATLAB software pair in present embodiment
The hydraulic self-strengthening method of submarine navigation device pressure-resistant material carries out simulation analysis.The mould in 1/4 section of cylinder is established in ANSYS
Type, size of mesh opening are set as 2mm, and displacement constraint is respectively set to two transversal cross-sections of cylinder, apply 40Mpa's in outer surface
Uniform load is analyzed according to two load steps of pressurization and unloading；
2, the radial direction during hydraulic Self-enhancement treatment and circumference stress emulation and theoretical comparative analysis.According to theory deduction
Relationship between obtained surrender radius and Self-enhancement treatment external pressure, can be calculated and be applied to shell in Self-enhancement treatment pressure
The radial and circumferential theoretical stress distribution of shell on external surface.External pressure is applied to using APDL parametric modeling [1] program
On outer surface in hydraulic autofrettage model, the radial direction and circumference stress distribution in hydraulic self-reinforcing process are obtained；
3, to the parameters of material such as yield strength, wall thickness, diameter ratio, different pressures have larger impact to self-reinforcing effect
Factor compare, obtain influence of the different parameters to material self-reinforcing effect, material bearing capacity after analysis self-reinforcing
Promotion effect, data are arranged and are summarized；
4, the foundation of mechanical self-reinforcing simulation model, by ABAQUS software to submarine navigation device in present embodiment
Pressure-resistant material machinery self-strengthening method carries out simulation analysis.Model is selected as 1/4 model of pressure hull, and carries out grid and draw
Point；
5, according to residual stress epicostal distribution with residual stress distribution on rib structure non-rib bone and by itself and nothing
The cylinder pressure hull machinery self-reinforcing process of rib structure is compared.The failure procedure of pressure hull mainly further includes structure
Unstability occurs, and after analyzing Self-enhancement treatment, the variation of the stability of structure.
With the increase of material yield strength it can be seen from Fig. 1 and Fig. 2, radial direction of the structure after Self-enhancement treatment and
The numerical value of circumferential residual stress is also increasing with it.
It is kept not it can be seen from Fig. 9 and Figure 10 in the internal diameter and outer diameter of pressure-resistant cylinder and elastic-plastic interface radius
Under the premise of change, with the increase of the yield strength of material, the maximum value of circumferential residual stress and the absolute value of minimum value are pressed
Increase according to linear change, this there will be great benefit to the pressure-bearing of pressure hull, so that pressure hull is bearing biggish work
When pressure, the stress distribution in wall thickness direction can be made more uniform, and the distribution for radial residual stress, maximum value is still
Directly proportional between yield strength, minimum value variation is not obvious.
From Fig. 2, Fig. 3 and Figure 11, Figure 12 as can be seen that as the numerical value of the increase residual stress of wall thickness increases therewith
Greatly, its wall thickness value cannot be too big for pressure hull, and not so can generate on the reserve buoyancy of aircraft greatly influences.From
To residual-stress value after Self-enhancement treatment of the cylinder of different wall thickness it can be concluded that, in material yield strength and inside diameter
Under the premise of certain, wall thickness is bigger, and produced residual stress is bigger after Self-enhancement treatment, and presentation direct proportion approximate with wall thickness
Relationship, but influence of the wall thickness for construction weight is excessive, when structural walls thicker than it is big when, negative effect in terms of brought weight
It is influenced much larger than brought by residual stress.
With the radial residual stress and ring after the hydraulic Self-enhancement treatment of increase of diameter ratio it can be seen from Fig. 5, Fig. 6
It is increased with it to the numerical value of residual stress, but there is no the variation of maximum value is so bright for the variation of residual stress minimum value
Aobvious, this for bearing the pressure hull of external pressure for being advantageous, because external compression stress itself is not for pressure-bearing
Benefit, and internal advantageous tensile stress can carry out offsetting greatly to cut down synthesis and answer to a greater extent with working stress
The numerical value of power.Diameter than be exactly for another angle thickness extension, in the case where internal diameter or outer diameter determine, wall thickness
Bigger, the effect after Self-enhancement treatment is better, therefore its promotion effect can be more obvious for the pressure hull of big depth.
The variation of circumferential residual stress becomes for same material it can be seen from Fig. 7, Fig. 8 and the pressure hull of structure
Gesture be first with elastic-plastic interface radius increase, the numerical value change of residual stress quickly, until elastic-plastic interface
Radius reach some numerical value after its numerical value it is just basicly stable.
The pressure hull of cylindrical band rib structure will not have a huge impact its stability after Self-enhancement treatment, with
Cylinder is identical without rib structure.Pressure hull can be illustrated pressure resistance can be improved after Self-enhancement treatment on the basis of original structure
For the intensity of shell structure without having an impact to its stability, this Self-enhancement treatment method can be adapted for pressure hull
Bearing capacity is promoted.
After adopting the above structure, present embodiment has the beneficial effect that one kind described in present embodiment is underwater
Aircraft pressure hull self-strengthening method, so that bearing capacity of submarine navigation device on the basis of original structure is greatly mentioned
The advantages that height, stability is good, and practicability is stronger, and the present invention has structure simple, and setting is reasonable, low manufacture cost.
The above is only used to illustrate the technical scheme of the present invention and not to limit it, and those of ordinary skill in the art are to this hair
The other modifications or equivalent replacement that bright technical solution is made, as long as it does not depart from the spirit and scope of the technical scheme of the present invention,
It is intended to be within the scope of the claims of the invention.
Claims (1)
1. a kind of submarine navigation device pressure hull self-strengthening method, it is characterised in that:
(1), the selection of material model:
Material model is simplified first before autofrettage model foundation, the method being often used is the modelling of deformable body；
Aluminum alloy materials are selected, belongs to the lesser material of hardenability, is analyzed using ideal elastoplastic model；
(2), traditional cylinder pressure hull structure cylindrical band rib structure, cylinder are analyzed without the intensity of rib structure, Jin Ergen
Cylindrical structure is obtained on the process shell wall thickness direction for bearing internal pressure and external pressure according to the elastic-plastic strain equation of cylindrical structure
Required external pressure in stress distribution law and generation elastic and plastic deformation process；
(3), according to, to the definition of residual stress, derived in the mechanics of materials occur elastic-plastic deformation cylinder lose external pressure
The regularity of distribution of its residual stress in wall thickness direction after power；
(4), using above-mentioned steps (2) and step (3) theory analysis as a result, by elastic-plastic interface radius and hydraulic self-reinforcing
Process processing pressure applies in mechanical self-reinforcing mode, derives between the magnitude of interference of formed punch and elastic-plastic interface radius
Relationship, hydraulic self-reinforcing process is obtained according to the relationship between the stress and strain of elastic-perfectly plastic material in loading procedure
Plastic-elastic stress Strain Distribution；
When cylinder bears external pressure, the relationship between radial displacement u and elastoplasticity radius and external pressure is as follows:
E is the elasticity modulus of cylinder in (formula 1), and μ is the Poisson's ratio of cylinder, and k is the diameter ratio b/a of cylinder；
When formed punch bears external pressure, for formed punch, since its material is harder, and yield strength is very high, thus in punching course
Its generation flexible deformation is available according to the relevant knowledge in Elasticity without being plastically deformed:
U in (formula 2)1For the elastic displacement of formed punch, E1For the elasticity modulus of formed punch, μ1For the Poisson's ratio of formed punch, a1For formed punch
Minimum diameter, b1For the outer diameter of formed punch, k1For the diameter ratio of formed punch；
Relational expression between simultaneous (formula 1) (formula 2) available magnitude of interference:
u1+u-b+a1=0 (formula 3)
(5), it obtaining most preferably surrendering radius, the stress value as caused by inner surface is all larger than the stress value at other positions of cylinder,
As receiving external pressure value p2And cylinder is in full yield situation, i.e. rpHave when=b:
P in formulajRequired limit external pressure value when occurring to be plastically deformed entirely for cylinder；
At this point, the equivalent stress of the residual stress at inner surface are as follows:
K in formulaj=rp/ a, k=b/a；
Above formula, which is unfolded, according to Taylor's formula to obtain:
This has formula (formula 7):
So as to obtain formula (formula 8):
So on the inner surface of cylinder, the equivalent stress of residual stress is negative value, in the expression formula of equivalent stress, works as circle
When cylinder reaches full yield situation, kj=k, bringing into formula can obtain:
Due toWhen, surrender completely will occur for material, it is therefore desirable toIt is available:
K≤2.218457489... is solved, it is possible thereby to know, as k≤2.218457489..., cylinder will not occur reversely
The phenomenon that surrender, and as k > 2.218457489..., cylinder can there is a phenomenon where reverse yieldings；
It enablesIt can be obtained when the relationship between the best plastic radius and diameter ratio of k > 2.218457489..., following institute
Show:
(6), bearing capacity theory lifting values after derivation Self-enhancement treatment, in external pressure p'2Under the action of, on cylindrical wall at radius r
Generated axial stress are as follows:
Radial stress are as follows:
Circumference stress are as follows:
It is available according to meter Sai Si Stress calculation formula, in external pressure p2Under effect, generated stress are as follows:
In view of the influence of residual stress, after carrying out Self-enhancement treatment as caused by residual stress and the external pressure born
Total meter Sai Si stress are as follows:
In formula:WithRespectively remaining radial stress and remaining circumference stress；
The stress of elastic region and plastic zone is calculated respectively；
Plastic zone:
The σ when plastic zone is surrendereds=σs, that is:
It solves:
Available by derivative concept, this formula is in rpMaximum value is obtained when=b, that is to say, that for diameter than the circle less than 2.2184
Cylinder, when all surrenders occur during Self-enhancement treatment, generated residual stress can improve pressure resistance to the greatest extent
The bearing capacity of shell, the also referred to as best surrender radius of this surrender radius, it is contemplated that the peace in pressure hull process
The requirement of full property and use environment cannot generally reach 100% full surrender, and be controlled at 50%~70%；
Elastic region:
It enablesI.e. obtained in the best plastic zone radius abovePressure-bearing energy after available Self-enhancement treatment
Power becomes:
Due in the cylinder without Self-enhancement treatment,When just have occurred that yield phenomenon, and
It can be seen that, bearing capacity improves twice after Self-enhancement treatment.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910204443.5A CN109949879B (en) | 2019-03-18 | 2019-03-18 | Self-reinforcing method for pressure-resistant shell of underwater vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910204443.5A CN109949879B (en) | 2019-03-18 | 2019-03-18 | Self-reinforcing method for pressure-resistant shell of underwater vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109949879A true CN109949879A (en) | 2019-06-28 |
| CN109949879B CN109949879B (en) | 2023-05-30 |
Family
ID=67010176
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910204443.5A Active CN109949879B (en) | 2019-03-18 | 2019-03-18 | Self-reinforcing method for pressure-resistant shell of underwater vehicle |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109949879B (en) |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101338817A (en) * | 2008-08-19 | 2009-01-07 | 朱瑞林 | Safe self-reinforcing pressure vessel |
| CN101655829A (en) * | 2009-09-14 | 2010-02-24 | 湖南师范大学 | External pressure self-intensification cylinder and design calculation and manufacturing method thereof |
| CN102563063A (en) * | 2011-12-27 | 2012-07-11 | 湖南师范大学 | Self-reinforcing pressure container based on safety design technical conditions |
| CN104455410A (en) * | 2014-11-14 | 2015-03-25 | 湖南师范大学 | External-pressure elastic differential-temperature-prestress external-heating self-enhanced pressure vessel |
| JP2016089891A (en) * | 2014-10-31 | 2016-05-23 | Ｊｆｅコンテイナー株式会社 | Accumulator and manufacturing method of accumulator |
| WO2016203924A1 (en) * | 2015-06-17 | 2016-12-22 | 臼井国際産業株式会社 | Steel pipe for fuel spray pipe and manufacturing method therefor |
| CN106326574A (en) * | 2016-08-27 | 2017-01-11 | 哈尔滨工业大学（威海） | Method for calculating extreme strength number based on welding deformation and residual stress |
| CN106446361A (en) * | 2016-09-08 | 2017-02-22 | 河海大学常州校区 | Tightness evaluation method of oil casing pipe screwed joint |
| CN109323058A (en) * | 2018-12-03 | 2019-02-12 | 宁波欧佩亚海洋工程装备有限公司 | A kind of glass fiber reinforcement bonding flexible pipe suitable for high external pressure environment |
-
2019
- 2019-03-18 CN CN201910204443.5A patent/CN109949879B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101338817A (en) * | 2008-08-19 | 2009-01-07 | 朱瑞林 | Safe self-reinforcing pressure vessel |
| CN101655829A (en) * | 2009-09-14 | 2010-02-24 | 湖南师范大学 | External pressure self-intensification cylinder and design calculation and manufacturing method thereof |
| CN102563063A (en) * | 2011-12-27 | 2012-07-11 | 湖南师范大学 | Self-reinforcing pressure container based on safety design technical conditions |
| JP2016089891A (en) * | 2014-10-31 | 2016-05-23 | Ｊｆｅコンテイナー株式会社 | Accumulator and manufacturing method of accumulator |
| CN104455410A (en) * | 2014-11-14 | 2015-03-25 | 湖南师范大学 | External-pressure elastic differential-temperature-prestress external-heating self-enhanced pressure vessel |
| WO2016203924A1 (en) * | 2015-06-17 | 2016-12-22 | 臼井国際産業株式会社 | Steel pipe for fuel spray pipe and manufacturing method therefor |
| CN106326574A (en) * | 2016-08-27 | 2017-01-11 | 哈尔滨工业大学（威海） | Method for calculating extreme strength number based on welding deformation and residual stress |
| CN106446361A (en) * | 2016-09-08 | 2017-02-22 | 河海大学常州校区 | Tightness evaluation method of oil casing pipe screwed joint |
| CN109323058A (en) * | 2018-12-03 | 2019-02-12 | 宁波欧佩亚海洋工程装备有限公司 | A kind of glass fiber reinforcement bonding flexible pipe suitable for high external pressure environment |
Non-Patent Citations (6)
| Title |
|---|
| HUNG-WENCHEN等: "Autofrettage analysis of a fibre-reinforced composite tube structure incorporated with a SMA", 《COMPOSITE STRUCTURES》 * |
| MITHILESH KUMAR DEWANGAN等: "Residual stress analysis of swage autofrettaged gun barrel via finite element method", 《JOURNAL OF MECHANICAL SCIENCE AND TECHNOLOGY》 * |
| POUYA BAHEMMAT等: "Enhancing retaining ring durability of high-speed generators using autofrettage process", 《THE 3RD CONFERENCE ON THERMAL POWER PLANTS》 * |
| RAHMAN SEIF: "Maximizing working pressure of autofrettaged three layer compound cylinders with considering Bauschinger effect and reverse yielding", 《MECCANICA》 * |
| 唐峰等: "基于 Mises 屈服条件的外压圆筒自增强研究", 《湖南师范大学自然科学学报》 * |
| 张于贤: "超高压容器中的自增强理论的研究及应用", 《中国优秀博硕士学位论文全文数据库 (博士) 工程科技Ⅱ辑》 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109949879B (en) | 2023-05-30 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN109163855A (en) | A kind of critical external compressive resistance performance test methods of pipelines in deep sea steel pipe | |
| Flores et al. | A fatigue analysis of a hydraulic Francis turbine runner | |
| Xinlong et al. | Overviews of investigation on submersible pressure hulls | |
| Hussain et al. | Vibration characteristics of fluid-filled functionally graded cylindrical material with ring supports | |
| Nejad et al. | Steady-state creep deformations and stresses in FGM rotating thick cylindrical pressure vessels | |
| Kamal et al. | Generalized Plane Strain Study of Rotational Autofrettage of Thick-Walled Cylinders—Part II: Numerical Evaluation | |
| Tang et al. | Tensile stiffness analysis on ocean dynamic power umbilical | |
| CN109949879A (en) | A kind of submarine navigation device pressure hull self-strengthening method | |
| CN117350125A (en) | Method, system and equipment for predicting fatigue performance of gas cylinder after dropping | |
| Wang et al. | Design and analysis on a model sphere made of maraging steel to verify the applicability of the current design code | |
| Yang et al. | Design of externally pressurized ellipsoidal heads with variable wall thicknesses | |
| Fakoor et al. | Comprehensive investigation of stress intensity factors in rotating disks containing three-dimensional semi-elliptical cracks | |
| Jung et al. | A study on buckling of filament-wound cylindrical shells under hydrostatic external pressure using finite element analysis and buckling formula | |
| Zhang et al. | Mechanical performance of bio-inspired bidirectional corrugated sandwich pressure shell under external hydrostatic pressure | |
| Perl et al. | The influence of the Bauschinger effect on 3D stress intensity factors for internal radial cracks in a fully or partially autofrettaged gun barrel | |
| Wang et al. | Topology optimization design of filling bodies in an umbilical based on moving morphable components theory | |
| Pranesh et al. | Structural Reinforcement of viewports in spherical pressure hull for manned submersibles | |
| Bae et al. | A study on integrated design for manufacturing processes of a compressed natural gas composite vessel | |
| CN107563592A (en) | A kind of multilayer non-adherent ocean flexible pipe limit torsional property fast appraisement method | |
| Forasassi et al. | Curved thin shell buckling behaviour | |
| Troiano et al. | 3d finite element modeling of the swage autofrettage process including the bauschinger effect | |
| Forasassi et al. | Buckling of imperfect thin cylindrical shell under lateral pressure | |
| Lin | Influence of Surface Crack Propagation on Ring-Shell Structure | |
| Govindaraj et al. | Comparative study of metallic and polymer composite shells for underwater vessels using FEA | |
| YE et al. | Calculation of marine propeller static strength based on coupled BEM/FEM |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |