CN115336415B - Rigidity-adjustable vibration-damping thrust bearing for ship - Google Patents
Rigidity-adjustable vibration-damping thrust bearing for ship Download PDFInfo
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- CN115336415B CN115336415B CN201110011862.0A CN201110011862A CN115336415B CN 115336415 B CN115336415 B CN 115336415B CN 201110011862 A CN201110011862 A CN 201110011862A CN 115336415 B CN115336415 B CN 115336415B
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- 238000013016 damping Methods 0.000 title claims description 43
- 238000002955 isolation Methods 0.000 claims abstract description 40
- 230000003068 static effect Effects 0.000 claims abstract description 11
- 239000003921 oil Substances 0.000 claims description 26
- 238000006073 displacement reaction Methods 0.000 claims description 14
- 230000005540 biological transmission Effects 0.000 claims description 5
- 239000010720 hydraulic oil Substances 0.000 claims description 5
- 230000006835 compression Effects 0.000 claims description 4
- 238000007906 compression Methods 0.000 claims description 4
- 230000010349 pulsation Effects 0.000 claims description 4
- 238000005259 measurement Methods 0.000 claims description 3
- 239000002184 metal Substances 0.000 claims description 3
- 230000001105 regulatory effect Effects 0.000 claims description 3
- 238000000926 separation method Methods 0.000 claims 1
- 230000000694 effects Effects 0.000 abstract description 5
- 230000005855 radiation Effects 0.000 abstract description 3
- 239000006096 absorbing agent Substances 0.000 abstract 1
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- 238000010586 diagram Methods 0.000 description 3
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- 230000009977 dual effect Effects 0.000 description 2
- 239000007789 gas Substances 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008094 contradictory effect Effects 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 229910052757 nitrogen Inorganic materials 0.000 description 1
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Abstract
A marine vibration reduction thrust bearing with adjustable rigidity is characterized in that an axial rubber vibration isolation block and a spring-air bag vibration absorber are arranged between a bearing structure in the bearing and a thrust bearing shell to isolate axial vibration of a shaft system, and static rigidity and dynamic rigidity of an axial vibration isolation system are adjusted through a piston and an air bag, so that the vibration isolation system can have a good vibration isolation effect in a wider bearing range. Meanwhile, a radial rubber vibration isolation block is arranged between the bearing inner force bearing structure and the bearing shell to isolate the radial vibration of the shafting. By the technical means, the vibration and noise radiation level of the whole ship, particularly the stern of the ship body, can be effectively reduced.
Description
The technical field is as follows:
the invention relates to a marine thrust bearing with a vibration reduction effect, which is mainly used for reducing vibration and noise of a water surface or underwater navigation body.
Background art:
generally, a ship shafting comprises a plurality of sections of shafts, each section of shaft has larger length and weight, certain eccentricity occurs during processing, deviation is inevitable during installation, slight bending deformation occurs during use, the eccentricity and the misalignment cause the shafting to be eccentric and misaligned, and the eccentricity and the misalignment cause vibration of the shafting and a ship body.
Furthermore, the propellers work in the wake of a non-uniform hull, and the forces acting on the shaft by the propellers, coupled with manufacturing and assembly variations, necessarily vary over time, which excites the shaft system to vibrate. This vibration excites the hull structure through the bearings into vibration which results in noise radiation and possibly fatigue failure of the hull structure. Since the rotating shaft needs to carry a great thrust force and transmit a great torque, it is difficult to perform vibration isolation on the shaft. The axial load generated by the propeller is borne by the thrust bearing, which causes the axial vibration generated by the propeller to be transmitted through the thrust bearing, so that the axial vibration of the shafting is necessary to be subjected to vibration isolation treatment at the thrust bearing.
The invention content is as follows:
the invention aims to reduce the transmission of ship shafting vibration to a main ship body, in particular to the vibration and noise of the ship body caused by shafting vibration generated by pulsating thrust, and provides a thrust bearing capable of effectively isolating the shafting vibration, thereby reducing the vibration and noise level of the whole ship, in particular the vibration and noise level of the stern of the ship body.
The present invention is made by using the basic structure of balance block type thrust bearing and adding vibration isolating structure. The schematic diagram of the rigidity-adjustable marine vibration-damping thrust bearing is shown in fig. 1, 3 and 6 (due to symmetry, only the upper half part is shown in fig. 1), and mainly comprises a thrust bearing shell 1, an axial vibration-damping block 2, a radial vibration-damping block 3, a bearing inner force-bearing structure 4, a thrust pad 5, a shaft 6, a spring 9, a hydraulic piston 10, an air bag 14 and a buffer tank 15, wherein the bearing inner force-bearing structure 4 uses a balance block supporting mode for the thrust pad 5. The spring 9, the hydraulic piston 10, the piston cavity 11, the air bag 14 and the buffer tank 15 form a spring-air bag vibration isolation system. The axial vibration isolation system is formed by connecting the axial vibration reduction block 2 and the spring-air bag vibration isolation system in parallel, or the axial vibration isolation system is formed by independently connecting one of the axial vibration reduction block 2 and the spring-air bag vibration isolation system, the axial vibration of the thrust bearing is isolated through the axial vibration isolation system, and the radial vibration of the thrust bearing is isolated through the radial vibration reduction block 3.
The axial damping mass 2 and the spring-air bag vibration isolation system correspond to a set of parallel springs. The hydraulic piston 10 functions to adjust the position of the spring 9. The lower part of the spring 9 is fixedly connected with a hydraulic piston 10, and the upper part of the spring 9 is fixedly connected with an upper spring panel 8. When the hydraulic piston 10 is positioned at the right end of the piston cavity 11 and is close to the hydraulic piston oil delivery port 12, the upper spring panel 8 is separated from the contact with the bearing inner force bearing structure 4, and the spring 9 does not work; when the hydraulic piston 10 is positioned at the left end of the piston cavity 11 close to the opening, the spring 9 bears the load to the maximum extent. The hydraulic piston 10 moves between the right end and the left end of the piston cavity 11 by adjusting the oil quantity of hydraulic oil in the piston cavity 11, so that the static stiffness of a parallel spring composed of the axial vibration reduction block 2 and the spring-air bag vibration isolation system is adjusted. The piston cavity 11 is connected with a buffer tank 15 through an oil pipe 13, and a buffer tank oil delivery port 16 at the other end of the buffer tank 15 is connected with a hydraulic system 23. The hydraulic system 23 is used for controlling the amount of hydraulic oil in the buffer tank 15 and the piston chamber 11. The air bag 14 and the buffer tank 15 form an oil path pulsating pressure control cavity which can control the pressure pulsation of the oil path of the thrust bearing to be transmitted to the hydraulic system 23 and can prevent the pressure pulsation of the hydraulic system 23 from being transmitted to the thrust bearing. The air bag 14 has the function that a damping spring is connected in series with the spring 9, the dynamic stiffness of the series spring formed by the spring 9 and the air bag 14 can be changed by adjusting the volume of gas in the air bag 14, and the dynamic stiffness of the parallel spring formed by the axial damping block 2 and the spring-air bag vibration isolation system can be further changed. Therefore, the static stiffness and the dynamic stiffness of the axial vibration isolation system are adjustable, and the system can have a good vibration isolation effect in a wider bearing range.
The axial vibration conduction process of the invention is as follows: when only the axial vibration-damping block 2 is used for vibration isolation, axial vibration of a ship shafting acts on the thrust pad 5 through the thrust disc 17 on the shaft 6, and then the vibration passes through the thrust pad 5, the bearing inner force-bearing structure 4, the axial vibration-damping block 2 and the thrust bearing shell 1 and is finally transmitted to a ship body; when only the spring-air bag vibration isolation system is used for vibration isolation, axial vibration of a ship shafting acts on the thrust pad 5 through the thrust disc 17 on the shaft 6, and then the vibration passes through the thrust pad 5, the bearing inner force bearing structure 4, the spring upper panel 8, the spring 9, the hydraulic piston 10, hydraulic oil in the piston cavity 11, the thrust bearing shell 1 and the buffer tank 15 and is finally transmitted to a ship body; when the axial damper mass 2 and the spring-air bag vibration isolation system are simultaneously active, axial vibrations are simultaneously conducted along the two paths described above. The radial vibration conduction process is as follows: the radial vibration of the ship shafting is transmitted to the bearing inner force-bearing structure 4 through the radial sliding contact surface 18 of the shaft 6 and the force-bearing structure 4, then transmitted to the ship body through the radial vibration reduction block 3 and the thrust bearing shell 1. As seen in the transmission process of shafting vibration, the vibration can be transmitted to the ship body only through the axial vibration isolation system and the radial vibration reduction block 3, and the effective isolation of the shafting vibration is realized.
The invention has the beneficial effects that: the thrust bearing capable of effectively isolating shafting vibration is provided, so that the vibration and noise radiation level of the whole ship, particularly the stern of a ship body, is reduced; the vibration isolation system has the function of adjusting the rigidity of the vibration isolation system, and has good vibration attenuation capacity in a wider bearing range; the vibration isolation structure is arranged on the thrust bearing shell which does not rotate together with the shaft, so that the problem that the vibration isolation and the force transmission are contradictory caused by the fact that the vibration isolation structure transmits torque is avoided.
Description of the drawings:
FIG. 1 is a schematic structural diagram of a single support damped thrust bearing.
Fig. 2 is a schematic structural diagram of a double-support vibration damping thrust bearing.
FIG. 3 isbase:Sub>A view A-A withbase:Sub>A spring and an axial damper block.
Figure 4 isbase:Sub>A viewbase:Sub>A-base:Sub>A containing onlybase:Sub>A plurality of axial damper blocks.
Figure 5 isbase:Sub>A viewbase:Sub>A-base:Sub>A containing only the annular axial damper block.
FIG. 6 is a view B-B of the damper with spring and axial damping mass and its connection to the surge tank.
Fig. 7 is a three-dimensional schematic view of the surge tank.
FIG. 8 is a schematic view of a single support dampened thrust bearing without a radial damper block.
FIG. 9 is a schematic view of a dual support dampened thrust bearing without a radial damper block.
In the drawings, 1. A thrust bearing housing; 2. an axial vibration damping mass; 3. a radial vibration damping mass; 4. the bearing inner bearing structure supports the thrust pad 5 as a balance block structure; 5. a thrust pad; 6. a shaft; 7. an axial sliding contact surface; 8. a spring upper panel; 9. a spring; 10. a hydraulic piston; 11. a piston cavity; 12. a hydraulic piston oil delivery port; 13. an oil pipe; 14. an air bag; 15. a buffer tank; 16. an oil delivery port of the buffer tank; 17. a thrust disc; 18. a radial sliding contact surface; 19. an oil outlet of the buffer tank; 20. a displacement detector; 21. an air bag vent; 22. an in-tank sensor; 23. a hydraulic system; 24. a pressure regulating device.
The specific implementation mode is as follows:
in the embodiment shown in fig. 1, the rigidity-adjustable marine vibration-damping thrust bearing mainly comprises a thrust bearing shell 1, an axial vibration-damping block 2, a radial vibration-damping block 3, a bearing inner force-bearing structure 4, a thrust pad 5, a shaft 6, a spring 9, a hydraulic piston 10 and a buffer tank 15. The axial vibration reduction block 2 and the radial vibration reduction block 3 are adhered in a groove in the thrust bearing shell 1, and the contact surfaces of the axial vibration reduction block 2 and the radial vibration reduction block 3 and the bearing inner force bearing structure 4 are not adhered. The axial vibration-damping block 2 and the radial vibration-damping block 3 adopt rubber vibration isolators, and can also be other types of vibration isolators. The axial vibration reduction block 2 and the spring 9 need to bear axial static load besides axial dynamic load, so that the bearing inner force-bearing structure 4 can slide along the axial direction. The radial damping block 3 needs to bear the weight of the bearing structure 4 and the shaft 6 in the bearing, so the radial damping block is installed in a pre-compression mode, namely the radial damping block 3 is in a compression state after the installation is finished. The spring 9 is fixed on a hydraulic piston 10, and the hydraulic piston 10 can slide in the piston cavity 11 by adjusting the amount of hydraulic oil in the piston cavity 11. A displacement detector 20 is arranged in the thrust bearing, and the position of the displacement detector is shown in fig. 1 and fig. 3 and is used for measuring the displacement between the bearing inner force-bearing structure 4 and the thrust bearing shell 1, the vibration of the bearing inner force-bearing structure 4 and the position of the hydraulic piston 10. The bearing inner force bearing structure 4 supports the thrust pad 5 by adopting a balance block structure. The shaft 6 is the only rotating part in the thrust bearing, the axial movement of the shaft is restrained by the thrust pad 5, the radial direction is restrained by the radial sliding contact surface 18 of the bearing inner force bearing structure 4, and the radial sliding contact surface 18 of the bearing inner force bearing structure 4 is a sliding bearing. The thrust bearing is lubricated by oil or water.
In the embodiment shown in fig. 1, each hydraulic piston oil delivery port 12 is connected with a buffer tank oil outlet 19 through an oil pipe 13, or two or even all hydraulic piston oil delivery ports 12 are connected with a buffer tank oil outlet 19 through an oil pipe 13 with a branch. The buffer tank oil delivery port 16 at the other end of the buffer tank 15 is connected with a hydraulic system 23. The oil pipe 13 adopts a hose or a metal wire-clamping rubber hose. At least two air bags 14 are arranged in the buffer tank 15, nitrogen or other non-combustible gas is filled in the air bags 14, the air inlet amount and the air pressure of the air bags can be adjusted through air bag air holes 21, and the air bag air holes 21 are connected with a pressure adjusting device 24. The air bag 14 is filled with static pressure of 0 MPa to 10 MPa through a pressure regulating device 24, and dynamic pressure of 0 Hz to 1000 Hz is loaded on the basis of the static pressure according to requirements. An in-tank sensor 22 is arranged in the buffer tank 15 to measure oil pressure or air pressure, a feedback control system is adopted to dynamically load pressure on the air bag 14 by combining the axial dynamic measurement result of the displacement detector 20, the dynamic stiffness of the air bag 14 is dynamically adjusted, and the spring-air bag vibration isolation system is actively controlled, so that the vibration isolation effect is further improved.
In the embodiment shown in fig. 1, the hydraulic piston 10 and the axial damping mass 2 are arranged at a distance, as shown in fig. 3. When the spring-air bag vibration isolation system is not needed and can meet the use requirement, only a plurality of axial vibration-damping blocks 2 (shown in figure 4) or one annular axial vibration-damping block 2 (shown in figure 5) can be arranged. The number of hydraulic pistons 10 and axial damping blocks 2 can be adjusted as desired, but still arranged symmetrically. In order to ensure the damping effect, the impedance of the contact part of the thrust bearing shell 1 and the axial damping block 2 is at least 3 times of the impedance of the axial damping block 2, the impedance of the contact part of the thrust bearing shell 1 and the radial damping block 3 is at least 3 times of the impedance of the radial damping block 3, the impedance of the piston cavity 11 is at least 3 times of the impedance of the spring 9, the impedance of the buffer tank 15 is at least 3 times of the impedance of the air bag 14, and hoses or metal wire-clamping rubber hoses are adopted to be connected with the thrust bearing and a hydraulic system before and after the air bag 14-the buffer tank 15.
In the embodiment shown in fig. 1, a displacement detector 20 is installed between the thrust bearing housing 1 and the bearing inner force-bearing structure 4, and the axial static load and the dynamic load of the shafting can be estimated according to the axial measurement result of the displacement detector 20, so that different vibration reduction schemes can be determined according to the magnitude and the property of the thrust load of the propeller. The displacement detector 20 can also measure the radial displacement of the bearing structure 4 in the bearing so as to conveniently monitor the radial vibration state of the thrust bearing.
In the embodiment shown in fig. 1, when the vehicle is in a forward state, the shaft 6 moves to the left due to the forward thrust, the right thrust disc 17 moves to the left along with the forward thrust and presses the right thrust pad 5, and an oil film is formed at the right axial sliding contact surface 7; the bearing inner force bearing structure 4 moves left to extrude the left axial vibration damping block 2 under the action of the right thrust pad 5 or extrude the spring 9 through the upper spring panel 8, and the deformation of the axial vibration damping block 2 or the spring 9 is balanced with the thrust to form a stable state; the thrust load is applied to the thrust bearing housing 1 via the axial damping mass 2 or spring 9, the hydraulic piston 10 and finally to the hull. When the vehicle is in a reverse state, the thrust transmission direction is opposite to that in a forward state.
The embodiment shown in fig. 2 is a dual support dampened thrust bearing having the same dampening structure as the embodiment shown in fig. 1.
In the embodiment shown in fig. 8, the radial damping mass 3 is not provided, so that the bearing inner force-bearing structure 4 is in direct contact with the thrust bearing housing 1, and the axial damping structure is the same as that of the embodiment shown in fig. 1.
In the embodiment shown in fig. 9, the radial damping mass 3 is not provided, so that the bearing inner force-bearing structure 4 is in direct contact with the thrust bearing housing 1, and the axial damping structure is the same as that of the embodiment shown in fig. 2.
Claims (6)
1. A rigidity-adjustable marine vibration reduction thrust bearing is composed of a thrust bearing shell (1), an axial vibration reduction block (2), a spring (9), a hydraulic piston (10), an air bag (14), a buffer tank (15), a radial vibration reduction block (3), a bearing inner force bearing structure (4), a built-in axial and radial displacement detector (20), a thrust pad (5) and a shaft (6), and is characterized in that an axial vibration isolation system is installed between the thrust bearing shell (1) and the bearing inner force bearing structure (4), the axial vibration isolation system is formed by connecting the axial vibration reduction block (2) and the spring-air bag vibration isolation system in parallel, wherein the axial vibration reduction block (2) is formed by embedding a rubber vibration isolator into the thrust bearing shell (1), the spring-air bag vibration isolation system is formed by connecting a spring-piston vibration isolator and an air bag (14) in series, the spring-piston vibration isolator and the air bag (14) use hydraulic oil as an acting force transmission medium, static pressure of 0 MPa to 10 MPa is filled in the air bag (14) through a pressure regulating device (24), and dynamic pressure of 0 Hz to 1000 Hz is loaded on the basis of the static pressure as required, so that an axial vibration isolation system formed by connecting different vibration isolators in parallel and in series is formed, the axial vibration isolation system can realize the adjustment of axial static stiffness and axial dynamic stiffness, and meets the shafting vibration and noise control requirements of a ship or a submarine under the condition that the axial thrust of a propeller greatly changes at different navigational speeds, the impedances of the thrust bearing shell (1) connected with the axial vibration reduction block (2), the spring-piston vibration isolator and the air bag (14), the bearing inner force bearing structure (4) and the buffer tank (15) are at least 3 times greater than the impedances of the axial vibration reduction block (2), the spring-piston vibration isolator and the air bag (14).
2. The marine vibration reduction thrust bearing with adjustable rigidity is composed of a thrust bearing shell (1), an axial vibration reduction block (2), a radial vibration reduction block (3), a bearing inner bearing structure (4), a built-in axial and radial displacement detector (20), a thrust pad (5) and a shaft (6), and is characterized in that the axial vibration reduction block (2) is installed between the thrust bearing shell (1) and the bearing inner bearing structure (4), the axial vibration reduction block (2) is formed by embedding a rubber vibration isolator into the thrust bearing shell (1), the axial vibration reduction block (2), the radial vibration reduction block (3) and the displacement detector (20) are adhered in a groove of the thrust bearing shell (1), and the thrust pad (5) is installed on the bearing inner bearing structure (4). The impedance of the thrust bearing shell (1) and the bearing inner force bearing structure (4) is at least 3 times greater than that of the axial vibration reduction block (2).
3. The marine vibration reduction thrust bearing with adjustable rigidity is characterized in that the radial vibration reduction block (3) is installed between the thrust bearing shell (1) and the bearing inner bearing structure (4), the radial vibration reduction block (3) is embedded into the thrust bearing shell (1) through a rubber vibration isolator, compression deformation generated according to the weight of the bearing inner bearing structure (4) is formed by adopting a pre-compression mode, the thrust bearing shell (1) connected with the radial vibration reduction block (3) and the bearing inner bearing structure (4) have impedance at least 3 times greater than that of the radial vibration reduction block (3), and therefore a radial vibration isolation system composed of the radial vibration reduction block (3) is formed, and radial vibration of a shafting is prevented from being transmitted to the thrust bearing shell (1).
4. The marine vibration-damping thrust bearing with adjustable rigidity according to claim 1, wherein a built-in axial and radial displacement detector (20) is arranged between the thrust bearing shell (1) and the bearing inner force-bearing structure (4), and the magnitude of axial static load and dynamic load of a shafting can be calculated according to the measurement result of the built-in axial and radial displacement detector (20), so that different vibration isolator combined vibration damping schemes can be determined according to the magnitude and the nature of the thrust load of a propeller.
5. The marine vibration-damping thrust bearing with adjustable rigidity according to claim 1, wherein the spring (9) is installed on the hydraulic piston (10), and the connection or the separation of the spring-air bag vibration isolation system and the bearing inner force-bearing structure (4) is controlled by adjusting the oil pressure of the hydraulic system (23), so that different vibration isolator combination vibration-damping schemes are determined according to the thrust of the propeller.
6. The marine vibration damping thrust bearing with adjustable rigidity according to claim 1, wherein the air bag (14) and the buffer tank (15) form an oil path pulsating pressure control cavity, hoses or metal wire-sandwiched rubber hoses are adopted to connect the hydraulic piston oil delivery port (12) and the hydraulic system (23) in front of and behind the air bag (14) and the buffer tank (15), and the oil path pulsating pressure control cavity can control the pressure pulsation of the oil path of the thrust bearing to be transmitted to the hydraulic system (23) and can prevent the pressure pulsation of the hydraulic system (23) from being transmitted to the thrust bearing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110011862.0A CN115336415B (en) | 2011-07-21 | 2011-07-21 | Rigidity-adjustable vibration-damping thrust bearing for ship |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110011862.0A CN115336415B (en) | 2011-07-21 | 2011-07-21 | Rigidity-adjustable vibration-damping thrust bearing for ship |
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| CN115336415B true CN115336415B (en) | 2015-12-23 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201110011862.0A Active CN115336415B (en) | 2011-07-21 | 2011-07-21 | Rigidity-adjustable vibration-damping thrust bearing for ship |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109278972A (en) * | 2018-08-30 | 2019-01-29 | 广州文冲船厂有限责任公司 | A kind of ship exhaust pipe rain-proof cap flexible type vibration insulation structure |
| CN114658798A (en) * | 2022-02-24 | 2022-06-24 | 中船澄西船舶修造有限公司 | Frequency modulation damping device and method for mounting marine auxiliary machinery equipment |
-
2011
- 2011-07-21 CN CN201110011862.0A patent/CN115336415B/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109278972A (en) * | 2018-08-30 | 2019-01-29 | 广州文冲船厂有限责任公司 | A kind of ship exhaust pipe rain-proof cap flexible type vibration insulation structure |
| CN109278972B (en) * | 2018-08-30 | 2024-02-23 | 广州文冲船厂有限责任公司 | Elastic vibration isolation structure of rain-proof cap of ship exhaust pipe |
| CN114658798A (en) * | 2022-02-24 | 2022-06-24 | 中船澄西船舶修造有限公司 | Frequency modulation damping device and method for mounting marine auxiliary machinery equipment |
| CN114658798B (en) * | 2022-02-24 | 2023-12-26 | 中船澄西船舶修造有限公司 | Frequency modulation damping device and damping method for installation of marine auxiliary equipment |
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