CN113848138A - A cyclic loading device for deep sea pipeline - Google Patents
A cyclic loading device for deep sea pipeline Download PDFInfo
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- CN113848138A CN113848138A CN202111108542.7A CN202111108542A CN113848138A CN 113848138 A CN113848138 A CN 113848138A CN 202111108542 A CN202111108542 A CN 202111108542A CN 113848138 A CN113848138 A CN 113848138A
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- 125000004122 cyclic group Chemical group 0.000 title claims abstract description 39
- 230000005540 biological transmission Effects 0.000 claims abstract description 55
- 238000012360 testing method Methods 0.000 claims abstract description 52
- 230000007246 mechanism Effects 0.000 claims abstract description 30
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 26
- 238000005452 bending Methods 0.000 claims abstract description 25
- 238000002347 injection Methods 0.000 claims abstract description 7
- 239000007924 injection Substances 0.000 claims abstract description 7
- 230000008859 change Effects 0.000 claims description 4
- 239000000126 substance Substances 0.000 claims description 2
- 230000000694 effects Effects 0.000 abstract description 4
- 238000013021 overheating Methods 0.000 abstract description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000001360 synchronised effect Effects 0.000 description 4
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000002474 experimental method Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 108010066057 cabin-1 Proteins 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
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Classifications
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
- G01N3/00—Investigating strength properties of solid materials by application of mechanical stress
- G01N3/32—Investigating strength properties of solid materials by application of mechanical stress by applying repeated or pulsating forces
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
- G01N3/00—Investigating strength properties of solid materials by application of mechanical stress
- G01N3/02—Details
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
- G01N2203/00—Investigating strength properties of solid materials by application of mechanical stress
- G01N2203/0001—Type of application of the stress
- G01N2203/0005—Repeated or cyclic
Abstract
The embodiment of the invention discloses a cyclic loading device for a deep sea pipeline, which comprises a test chamber, an axial cyclic loading mechanism and a bending moment cyclic loading mechanism, wherein the axial cyclic loading mechanism is arranged on the test chamber; the test chamber is provided with a water injection port, a water outlet and an exhaust port which can be opened or closed; the axial circulating loading mechanism comprises an axial force transmission rod and a first eccentric structure, wherein one end of the axial force transmission rod extends into the test chamber and extends along the axial direction of the test chamber, and the first eccentric structure is connected to the other end of the axial force transmission rod and is positioned outside the test chamber and used for pushing the axial force transmission rod along the axial direction; the bending moment circulating loading mechanism comprises a transmission support and a second eccentric structure, wherein the transmission support is positioned in the test chamber and can be sleeved with a pipeline to be tested, the second eccentric structure is positioned outside the test chamber, and the transmission support is connected with the second eccentric structure through a radial transmission rod assembly movably arranged along the radial direction. The effect of high-frequency and cyclic loading can be effectively achieved under the high-pressure water environment, and the overheating problem caused by the adoption of a hydraulic device in the prior art can be avoided.
Description
Technical Field
The embodiment of the invention relates to the technical field of loading devices of deep sea pipelines, in particular to a circulating loading device for a deep sea pipeline.
Background
With the increase of the development of ocean oil and gas resources, a large number of deep sea pipelines are laid and put into use, and in order to ensure the operation stability and safety of the pipelines and research the buckling and crushing mechanism of the pipelines, a pipeline crushing scale ratio test simulating the deep sea environment is required to be carried out. Whether the mode of applying load to the pipeline and the type of applying load accord with the real deep sea environment or not directly influences the reliability and accuracy of the test result. At present, most of test devices for applying load to test pipelines in a high-pressure water tank control force through an oil press, and the axial force application is limited. Therefore, the invention provides a test device which can realize cyclic high-frequency application of load by controlling displacement, ensure the accuracy and reliability of the test and provide reliable basis for field construction.
Disclosure of Invention
Therefore, the embodiment of the invention provides a cyclic loading device for a deep sea pipeline, which is used for circularly applying bending moment and axial force to the deep sea pipeline based on an eccentric structure to truly simulate the stress condition of the submarine pipeline, and meanwhile, the application of force by adopting the eccentric structure can effectively achieve the effect of high-frequency cyclic loading under a high-pressure water environment, and the overheating problem caused by adopting a hydraulic device in the prior art can not occur.
In order to achieve the above object, an embodiment of the present invention provides the following:
in one aspect of an embodiment of the invention, a cyclic loading device for a deep sea pipeline is provided, which comprises a test cabin, an axial cyclic loading mechanism and a bending moment cyclic loading mechanism, wherein the axial cyclic loading mechanism and the bending moment cyclic loading mechanism are respectively at least partially positioned in the test cabin; wherein the content of the first and second substances,
the test chamber is provided with a water injection port, a water outlet and an exhaust port which can be opened or closed;
the axial cyclic loading mechanism comprises an axial force transmission rod and a first eccentric structure, wherein one end of the axial force transmission rod extends into the test chamber and extends along the axial direction of the test chamber, and the first eccentric structure is connected to the other end of the axial force transmission rod and is positioned outside the test chamber and used for pushing the axial force transmission rod along the axial direction;
the bending moment circulating loading mechanism comprises a transmission support and a second eccentric structure, wherein the transmission support is positioned in the test chamber and can be sleeved with a pipeline to be tested, the second eccentric structure is positioned outside the test chamber, and the transmission support is connected with the second eccentric structure through a radial transmission rod assembly movably arranged along the radial direction.
As a preferable scheme of the present invention, the first eccentric structure includes a first eccentric wheel assembly, and a first driving member for driving the first eccentric wheel assembly to rotate, one end of the axial force transmission rod is connected to the first eccentric wheel assembly, and the other end of the axial force transmission rod extends into the test chamber, and the first driving member drives the axial force transmission rod to reciprocate along the axial direction through the first eccentric wheel assembly.
As a preferable scheme of the present invention, the second eccentric structure includes a second eccentric wheel assembly, and a second driving member for driving the second eccentric wheel assembly to rotate, and the second eccentric wheel assembly is connected to the transmission bracket through a piston rod and a bending moment transmission rod which are sequentially connected.
As a preferable mode of the present invention, the transmission bracket includes a first support plate and a second support plate sequentially arranged along an axial direction of the test chamber, and the first support plate and the second support plate are formed with through holes which are coaxial and are the same as the axial direction of the test chamber, and the first support plate and the second support plate are connected to the bending moment transmission rod through a connecting plate.
As a preferable scheme of the present invention, the water injection port and the water outlet are located at one side of the test chamber close to the bottom, the water injection port and the water outlet are respectively located at two ends of the test chamber, and the air exhaust port is located at one side of the test chamber close to the top.
As a preferable scheme of the present invention, two ends of the test chamber may be provided with a chamber cover in an opening or closing manner, and the chamber cover is detachably connected with a flange for fixing a pipeline to be tested.
As a preferable mode of the present invention, the first driving member and the second driving member are cooperatively formed as a driving assembly, the driving assembly includes a servo motor, and a steering speed changing assembly extending outward from an output rod of the servo motor, and at least one of the first eccentric wheel assembly and the second eccentric wheel assembly is connected to the servo motor through the steering speed changing assembly.
In a preferred embodiment of the present invention, the second eccentric wheel assembly is connected to an end of an output rod of the servo motor, and the first eccentric wheel assembly is connected to the steering transmission assembly.
As a preferable scheme of the present invention, the steering and speed changing assembly includes a first bevel gear sleeved on an output rod of the servo motor, and a second bevel gear engaged with the first bevel gear and capable of rotating, and the second bevel gear is provided with a rotating rod, the rotating rod is sleeved with a plurality of driving wheels along an axial direction, a driving rod penetrates through the second eccentric wheel assembly, the driving rod is sleeved with a plurality of driven wheels having outer surfaces respectively engaged with the driving wheels along the axial direction, a clamping groove is formed between the driven wheels and the driving rod, and the driving rod is provided with a clamping block capable of being clamped in the clamping groove in a sliding manner.
The embodiment of the invention has the following advantages:
the eccentric structure is adopted to drive the transmission rod to reciprocate, so that the axial and bending moment loading of the pipeline to be tested is realized, the frequency of applied load can be effectively improved, and the problem of overheating of the device is avoided; meanwhile, the circulating loading of the pipeline to be tested under the high-pressure water environment is effectively realized through the matched arrangement of the test chamber, and effective condition support is provided for the simulation experiment of the deep sea pipeline.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below. It should be apparent that the drawings in the following description are merely exemplary, and that other embodiments can be derived from the drawings provided by those of ordinary skill in the art without inventive effort.
The structures, ratios, sizes, and the like shown in the present specification are only used for matching with the contents disclosed in the specification, so as to be understood and read by those skilled in the art, and are not used to limit the conditions that the present invention can be implemented, so that the present invention has no technical significance, and any structural modifications, changes in the ratio relationship, or adjustments of the sizes, without affecting the effects and the achievable by the present invention, should still fall within the range that the technical contents disclosed in the present invention can cover.
Fig. 1 is a schematic structural diagram of a cyclic loading device according to an embodiment of the present invention;
fig. 2 is a schematic diagram of an internal structure of a cyclic loading device according to an embodiment of the present invention;
FIG. 3 is a schematic structural diagram of a bending moment cyclic loading mechanism according to an embodiment of the present invention;
FIG. 4 is a schematic structural diagram of an axial cyclic loading mechanism according to an embodiment of the present invention;
FIG. 5 is a partial schematic structural view of a steering shifting assembly according to an embodiment of the present invention;
fig. 6 is a partial cross-sectional view of a drive rod and driven wheel provided by an embodiment of the present invention.
In the figure:
1-a test chamber; 2-an axial cyclic loading mechanism; 3-bending moment cyclic loading mechanism; 4-a pipeline to be tested;
11-a water injection port; 12-a water outlet; 13-an exhaust port; 14-cabin body support; 15-a front hatch; 16-a rear hatch; 17-a flange;
21-axial force transmission rod; 22-a first eccentric wheel assembly; 23-a first drive member; 24-a first bearing; 25-a motor support;
31-a transmission bracket; 32-a radial drive rod assembly; 33-a second eccentric configuration;
311-a first plate; 312-a second plate; 313-perforation; 314-a link plate;
321-a second eccentric wheel assembly; 322-a second drive member; 323-piston rod; 324-moment drive rod; 325-a second bearing;
51-a servo motor; 52-output rod; 53-first bevel gear; 54-a second bevel gear; 55-rotating rod; 56-driving wheel; 57-a drive rod; 58-driven wheel; 59-card slot.
Detailed Description
The present invention is described in terms of particular embodiments, other advantages and features of the invention will become apparent to those skilled in the art from the following disclosure, and it is to be understood that the described embodiments are merely exemplary of the invention and that it is not intended to limit the invention to the particular embodiments disclosed. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
As shown in fig. 1 to 6, the present invention provides a cyclic loading device for deep sea pipelines, and in particular, a structure comprising a test chamber 1, a water inlet 11, a water outlet 12 and an air outlet 13 are formed on a chamber body of the test chamber 1, and a front chamber cover 15 and a rear chamber cover 16 are formed on the chamber body and located at the front end and the rear end respectively, so that the whole chamber body can be formed into an internally closed space by the front chamber cover 15 and the rear chamber cover 16; a cabin bracket 14 for supporting is arranged below the cabin and is used for fixing the spatial position of the cabin. In the experimental process, the pipeline 4 to be tested is pushed into the cabin body, the pipeline 4 to be tested sequentially penetrates through the through holes 313 in the first supporting plate 311 and the second supporting plate 312 on the transmission support 31, the transmission support 31 is located in the middle of the pipeline 4 to be tested, the flange 17 is welded to the two ends of the pipeline 4 to be tested, the front end of the pipeline is fixedly connected with the front cabin cover 15 through the flange 17 and the screws, the flange 17 connected with the axial force transmission rod 21 is fixedly connected with the rear end of the pipeline 4 to be tested through the screws, and the installation of the test cabin 1 in the whole test state is completed. Of course, the axial force transmission rod 21 can be connected to the flange 17 by a sleeve structure, so that a certain movement gap can be provided between the axial force transmission rod 21 and the flange 17, thereby effectively achieving the axial pushing of the axial force transmission rod 21.
In the experiment process, the exhaust port 13 is opened, water is injected into the test chamber 1 through the water injection port 11, air in the chamber body is discharged, the chamber body is filled with liquid, and the liquid in the chamber body is discharged through the water outlet 12 after the experiment is finished. Axial force loading is carried out on the pipeline 4 to be tested through the axial circulating loading mechanism 2, and bending moment loading is carried out on the pipeline 4 to be tested through the bending moment circulating loading mechanism 3.
Further, the bending moment cyclic loading mechanism 3 includes a transmission bracket 31, a bending moment transmission rod 324, a piston rod 323, a second bearing 325, a second eccentric wheel assembly 321, a second driving member 322 and a motor bracket 25. The transmission bracket 31 is connected with the piston rod 323 through the bending moment transmission rod 324, the second bearing 325 connects the piston rod 323 with the second eccentric wheel assembly 321, the second driving member 322 (specifically, a servo motor can be selected) drives the second eccentric wheel assembly 321 to rotate, and the motor bracket 25 is located below the second driving member 322 to fix the spatial position thereof.
In a more preferred embodiment of the present invention, the axial cyclic loading mechanism 2 includes a first eccentric wheel assembly 22, a first driving member 23, an axial force transmission rod 21, a first bearing 24 and a motor bracket 25. The axial force transmission rod 21 is connected with the pipeline 4 to be tested through the flange 17 and connected with the first eccentric wheel component 22 through the piston rod piece and the first bearing 24, the first driving piece 23 drives the first eccentric wheel component 22 to rotate, and the motor support 25 is positioned below the first driving piece 23 and fixes the spatial position of the first driving piece 23.
It should be noted that the first eccentric wheel assembly 22 and the second eccentric wheel assembly 321 may be arranged in a manner understood by those skilled in the art, and may include, for example, an eccentric wheel and a hinge member hinged to the eccentric wheel and not coaxial with the rotating shaft, and a piston rod member connected to the hinge member and further hinged to the axial force transmission rod 21 or the bending moment transmission rod 324 to apply the reciprocating force.
In order to achieve the synchronous operation of the axial cyclic loading mechanism 2 and the bending moment cyclic loading mechanism 3, and at the same time, to achieve the synchronous operation effect effectively through a mechanical manner without additionally adding a synchronous control system, in a more preferred embodiment, the first driving member 23 and the second driving member 322 are cooperatively formed as a driving assembly, the driving assembly includes a servo motor 51, and a steering speed change assembly extending outwards from an output rod 52 of the servo motor 51, and at least one of the first eccentric wheel assembly 22 and the second eccentric wheel assembly 321 is connected to the servo motor 51 through the steering speed change assembly. Meanwhile, through the arrangement of the steering speed change assembly, the frequency of at least one of the axial cyclic loading mechanism 2 and the bending moment cyclic loading mechanism 3 can be further adjusted, and the relative adjustment of the axial cyclic loading mechanism 2 and the bending moment cyclic loading mechanism 3 is realized.
In a preferred embodiment, the second eccentric wheel assembly 321 is connected to the end of the output rod 52 of the servo motor 51, and the first eccentric wheel assembly 22 is connected to the steering gear shifting assembly. One of the steering gear shifting components is connected with the steering gear shifting component, so that the relative difficulty of overall adjustment is further reduced on the basis of effectively realizing relative synchronous adjustment of the steering gear shifting component and the steering gear shifting component.
Of course, in order to realize multi-gear adjustment, in a more preferred embodiment of the present invention, the steering and speed changing assembly includes a first bevel gear 53 sleeved on the output rod 52 of the servo motor 51, and a second bevel gear 54 engaged with the first bevel gear 53 and rotatably disposed, and the second bevel gear 54 is provided with a rotating rod 55, the rotating rod 55 is sleeved with a plurality of driving wheels 56 along an axial direction, the second eccentric wheel assembly 321 is penetrated with a driving rod 57, the driving rod 57 is sleeved with a plurality of driven wheels 58 whose outer surfaces are respectively engaged with the driving wheels 56 along the axial direction, a slot 59 is formed between the driven wheels 58 and the driving rod 57, and the driving rod 57 is slidably provided with a latch capable of being latched in the slot 59.
The servo motor is used for driving the eccentric wheel structure to move, so that the frequency of applied load is improved, and the problem of overheating of the hydraulic device is solved; meanwhile, based on the further arrangement of the test chamber 1, the cyclic loading of the axial force and the bending moment of the pipeline is realized in the environment with high-pressure water. Further, the invention is based on the arrangement of the eccentric wheel structure, and can realize high-frequency vibration by controlling the movement on the eccentric wheel.
Although the invention has been described in detail above with reference to a general description and specific examples, it will be apparent to one skilled in the art that modifications or improvements may be made thereto based on the invention. Accordingly, such modifications and improvements are intended to be within the scope of the invention as claimed.
Claims (9)
1. A cyclic loading device for deep sea pipelines is characterized by comprising a test cabin (1), an axial cyclic loading mechanism (2) and a bending moment cyclic loading mechanism (3) which are at least partially positioned in the test cabin (1); wherein the content of the first and second substances,
a water injection port (11), a water outlet (12) and an exhaust port (13) which can be opened or closed are formed on the test chamber (1);
the axial cyclic loading mechanism (2) comprises an axial force transmission rod (21) with one end extending into the test chamber (1) and extending along the axial direction of the test chamber (1), and a first eccentric structure which is connected to the other end of the axial force transmission rod (21) and is positioned outside the test chamber (1) and used for pushing the axial force transmission rod (21) along the axial direction;
the bending moment circulating loading mechanism (3) comprises a transmission support (31) which is positioned in the test chamber (1) and can be sleeved with a pipeline (4) to be tested, and a second eccentric structure (33) which is positioned outside the test chamber (1), and the transmission support (31) is connected with the second eccentric structure (33) through a radial transmission rod assembly (32) movably arranged along the radial direction.
2. A cyclic loading device according to claim 1, wherein the first eccentric structure comprises a first eccentric wheel assembly (22), a first driving member (23) for driving the first eccentric wheel assembly (22) to rotate, one end of the axial force transmission rod (21) is connected to the first eccentric wheel assembly (22), the other end of the axial force transmission rod extends into the test chamber (1), and the first driving member (23) drives the axial force transmission rod (21) to reciprocate along the axial direction through the first eccentric wheel assembly (22).
3. A cyclical loading device according to claim 2, wherein the second eccentric structure (33) comprises a second eccentric wheel assembly (321), a second driving member (322) for driving the second eccentric wheel assembly (321) to rotate, and the second eccentric wheel assembly (321) is connected to the transmission bracket (31) through a piston rod (323) and a bending moment transmission rod (324) which are connected in sequence.
4. A cyclical loading device according to claim 3, wherein the transmission bracket (31) comprises a first support plate (311) and a second support plate (312) which are arranged in sequence along the axial direction of the test chamber (1), and the first support plate (311) and the second support plate (312) are provided with through holes (313) which are coaxial and have the same axial direction as the test chamber (1), and the first support plate (311) and the second support plate (312) are connected with the bending moment transmission rod (324) through a connecting plate (314).
5. A cyclic loading device according to claim 1 or 2, wherein the water inlet (11) and the water outlet (12) are located on the side of the test chamber (1) near the bottom, the water inlet (11) and the water outlet (12) are respectively located at two ends of the test chamber (1), and the air outlet (13) is located on the side of the test chamber (1) near the top.
6. A cyclic loading device according to claim 5, characterized in that the test chamber (1) is provided with a cover which can be opened or closed at both ends, and a flange (17) for fixing the pipeline (4) to be tested is detachably connected to the cover.
7. A cyclical loading device according to claim 3, wherein the first driving member (23) and the second driving member (322) are cooperatively formed as a driving assembly comprising a servo motor (51) and a steering gear shifting assembly extending outwardly from an output shaft (52) of the servo motor (51), and wherein at least one of the first eccentric wheel assembly (22) and the second eccentric wheel assembly (321) is coupled to the servo motor (51) via the steering gear shifting assembly.
8. A cyclical loading device according to claim 7, wherein the second eccentric wheel assembly (321) is connected to the end of the output rod (52) of the servo motor (51) and the first eccentric wheel assembly (22) is connected to the steering and transmission assembly.
9. A cyclical loading device according to claim 8, wherein the steering and speed change assembly comprises a first bevel gear (53) journalled on the output rod (52) of the servomotor (51), a second bevel gear (54) which is engaged with the first bevel gear (53) and is provided to be rotatable, a rotating rod (55) is arranged on the second bevel gear (54), a plurality of driving wheels (56) are sleeved on the rotating rod (55) along the axial direction, a driving rod (57) penetrates through the second eccentric wheel component (321), a plurality of driven wheels (58) with outer surfaces respectively meshed with the driving wheel (56) are sleeved on the driving rod (57) along the axial direction, a clamping groove (59) is formed between the driven wheel (58) and the driving rod (57), the driving rod (57) is provided with a clamping block capable of being clamped in the clamping groove (59) in a sliding manner.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111108542.7A CN113848138A (en) | 2021-09-22 | 2021-09-22 | A cyclic loading device for deep sea pipeline |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111108542.7A CN113848138A (en) | 2021-09-22 | 2021-09-22 | A cyclic loading device for deep sea pipeline |
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| CN113848138A true CN113848138A (en) | 2021-12-28 |
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| CN202111108542.7A Pending CN113848138A (en) | 2021-09-22 | 2021-09-22 | A cyclic loading device for deep sea pipeline |
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102175437A (en) * | 2011-01-14 | 2011-09-07 | 天津大学 | Buckling test device for deepwater submarine conduit |
| CN106442181A (en) * | 2016-09-16 | 2017-02-22 | 天津大学 | Fatigue test device for marine riser external corrosion |
| CN106525618A (en) * | 2016-09-22 | 2017-03-22 | 天津大学 | Flow corrosion testing device under axial fatigue load of scaling marine pipeline |
| CN109342177A (en) * | 2018-11-20 | 2019-02-15 | 大连理工大学 | A kind of full-scale pipeline deep-sea complexity ocean environmental loads combination loading pilot system |
| CN110196156A (en) * | 2019-03-12 | 2019-09-03 | 天津大学 | A kind of deep-sea pipeline Complicated Loads combination loading test method |
| CN111426547A (en) * | 2020-04-23 | 2020-07-17 | 中国船舶科学研究中心 | Flexible pipeline bending coupling nondestructive loading test device and use method thereof |
| CN113237766A (en) * | 2021-04-22 | 2021-08-10 | 天津大学 | Pipeline pressure chamber loading system capable of loading multiple loads simultaneously |
-
2021
- 2021-09-22 CN CN202111108542.7A patent/CN113848138A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102175437A (en) * | 2011-01-14 | 2011-09-07 | 天津大学 | Buckling test device for deepwater submarine conduit |
| CN106442181A (en) * | 2016-09-16 | 2017-02-22 | 天津大学 | Fatigue test device for marine riser external corrosion |
| CN106525618A (en) * | 2016-09-22 | 2017-03-22 | 天津大学 | Flow corrosion testing device under axial fatigue load of scaling marine pipeline |
| CN109342177A (en) * | 2018-11-20 | 2019-02-15 | 大连理工大学 | A kind of full-scale pipeline deep-sea complexity ocean environmental loads combination loading pilot system |
| CN110196156A (en) * | 2019-03-12 | 2019-09-03 | 天津大学 | A kind of deep-sea pipeline Complicated Loads combination loading test method |
| CN111426547A (en) * | 2020-04-23 | 2020-07-17 | 中国船舶科学研究中心 | Flexible pipeline bending coupling nondestructive loading test device and use method thereof |
| CN113237766A (en) * | 2021-04-22 | 2021-08-10 | 天津大学 | Pipeline pressure chamber loading system capable of loading multiple loads simultaneously |
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