CN115408833A - Grillage superstructure design method suitable for low-frequency vibration isolation of ship mechanical equipment - Google Patents

Grillage superstructure design method suitable for low-frequency vibration isolation of ship mechanical equipment Download PDF

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CN115408833A
CN115408833A CN202210972973.6A CN202210972973A CN115408833A CN 115408833 A CN115408833 A CN 115408833A CN 202210972973 A CN202210972973 A CN 202210972973A CN 115408833 A CN115408833 A CN 115408833A
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superstructure
plate frame
grillage
ship
local
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李应刚
陈鼎康
李洵语
胡蜜
李晓彬
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Wuhan University of Technology WUT
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Wuhan University of Technology WUT
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    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/20—Design reuse, reusability analysis or reusability optimisation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T90/00—Enabling technologies or technologies with a potential or indirect contribution to GHG emissions mitigation

Abstract

The invention relates to a grillage superstructure design method suitable for low-frequency vibration isolation of marine mechanical equipment, which comprises the following steps of: determining a required vibration isolation frequency range; aiming at the hull plate frame structure, local resonators are arranged at intervals in the crossed area of the longitudinal reinforcing ribs and the transverse reinforcing ribs; respectively establishing a hull plate frame superstructure primitive cell model and a hull plate frame superstructure limited period model, obtaining an energy band structure of the hull plate frame superstructure through the hull plate frame superstructure primitive cell model, outputting a vibration transmission characteristic curve through the hull plate frame superstructure limited period model, and verifying the correctness of the band gap position and the width; determining the structural size of a hull grillage superstructure; a local resonator is additionally arranged on the hull plate frame structure between the vibration source and the protection area; and verifying the effectiveness of the arrangement mode of the local resonators. The invention realizes effective isolation of low-frequency and medium-frequency vibration noise below 500Hz of marine mechanical equipment, and can realize vibration reduction in a specific frequency range by designing the size and the interval of the local resonators.

Description

Grillage superstructure design method suitable for low-frequency vibration isolation of ship mechanical equipment
Technical Field
The invention belongs to the technical field of vibration isolation of ship mechanical equipment, and particularly relates to a grillage superstructure design method suitable for low-frequency vibration isolation of ship mechanical equipment.
Background
The marine traffic industry is developed vigorously, and the problem of ship vibration radiation noise pollution is also becoming more severe. The ship vibration noise not only influences the normal rest and work of the crew, but also easily damages the hearing system, possibly causing the symptoms of noise deafness, hypomnesis and the like. The International Maritime Organization (IMO) in 2014 puts higher requirements on ship design and vibration and noise reduction performance through 'ship-borne noise level rules'.
The ship vibration noise excitation source mainly comprises mechanical excitation, propeller excitation and wave excitation, and has the characteristics of large power and wide spectrum distribution range. The mechanical noise excitation source mainly transmits vibration in a low-frequency bending wave form in a hull plate frame structure and radiates noise to air and water, and the comfort and the concealment of the vibration noise of the ship are seriously influenced. At present, the ship vibration damping and noise reduction technology mainly comprises a passive control technology and an active control technology. Passive control techniques can reduce the magnitude of the full-band vibration, but are still very challenging in terms of low-frequency vibration line spectrum control. The active control technology is an effective means for low-frequency vibration line spectrum control, but the active control technology has the technical bottleneck problems of system stability, reliability, environmental adaptability and the like, and a lot of researches are still in the test stage and are not widely applied to engineering.
In order to realize the purpose of vibration isolation of a low-frequency section of a ship mechanical equipment structure, a phononic crystal structure capable of realizing local resonance can be introduced into the structural design of a ship plate frame. The phononic crystal structure is a medium formed by periodically arranging and compounding primitive cell materials in space, and the structure has forbidden band characteristics, namely, elastic waves (vibration waves or sound waves) in a certain frequency range cannot be continuously transmitted through the phononic crystal. The band gap characteristics of different frequency bands can be adjusted by changing the material properties, the combination mode, the periodic distribution and other modes. When the elastic wave in the forbidden band frequency range enters the superstructure, the elastic wave in the forbidden band cannot continuously propagate through the structure due to the scattering effect or the local resonance effect of the internal periodic structure of the superstructure to form an elastic wave forbidden band. The proposal of the phononic crystal structure concept provides a new idea for solving the problems of structure low-frequency vibration and radiation noise control.
Chinese patent CN2020108446478 discloses a bearing and vibration isolation integrated plate shell superstructure and a design method thereof, wherein the plate shell superstructure comprises a plate shell and a plurality of microstructure components; the microstructure component is a block structure with equal section, the section contour line of the microstructure component is composed of a bottom edge and two arcsine-like function curves, and the intersection point of the two arcsine-like function curves forms a beak tip; the bottom surfaces of the microstructure components are connected with the plate shell; the microstructure components are periodically arranged to form an array to separate the vibration source and the protected object. When the elastic wave excited by the vibration source is transmitted to the periphery of the array from any direction along the plate shell, the microstructure component generates bending and torsional vibration under the influence of the elastic wave, and the microstructure can generate force and moment effects on the plate shell, so that the transmission of the elastic wave in the plate shell is inhibited, and the isolation of the incident elastic wave in any direction of a high-frequency band in the plate shell is realized. Simple structure, processing is convenient, can keep apart by protection object and vibration source simultaneously, has good bearing and vibration isolation ability concurrently. However, the following disadvantages still exist: the microstructure components are complex, and the requirement on processing precision is high; the design method mainly aims at the light plate structure, has poor applicability to a more complex hull plate frame structure, mainly aims at the vibration isolation of medium and high frequency band elastic waves, and cannot realize effective isolation of the medium and low frequency elastic waves in the ship.
Disclosure of Invention
The technical problem to be solved by the invention is to provide a grillage superstructure design method suitable for low-frequency vibration isolation of ship mechanical equipment aiming at the defects in the prior art, so that the low-frequency vibration noise in the ship mechanical equipment can be effectively isolated on the basis of not changing the structure of a hull basic grillage to ensure the strength, rigidity, stability and reliability of the hull basic grillage, and the vibration and underwater radiation noise can be reduced in the whole ship range.
The technical scheme adopted by the invention for solving the technical problems is as follows:
a grillage superstructure design method suitable for low-frequency vibration isolation of marine mechanical equipment comprises a hull grillage structure and additional periodically arranged local area resonators, and comprises the following steps:
s1, analyzing a vibration excitation source of typical mechanical equipment of a ship, and determining a required vibration isolation frequency range;
s2, aiming at the hull plate frame structure, considering the continuity of the model, arranging local resonators at intervals in the crossed area of the longitudinal reinforcing ribs and the transverse reinforcing ribs; respectively establishing a hull plate frame superstructure primitive cell model and a hull plate frame superstructure finite period model;
s3, applying Floquet periodic boundary conditions in the X direction and the y direction of the original cell model of the ship hull plate frame superstructure, performing parameter scanning along wave vectors in the gamma-X-M-gamma direction, solving eigenmodes and eigenfrequencies of the structure under each wave vector, and obtaining an energy band structure of the ship hull plate frame superstructure by taking the wave vector direction as a horizontal coordinate and the eigenfrequencies as a vertical coordinate; applying acceleration excitation to simulate vibration source vibration on the left side of a ship hull plate frame superstructure finite period model, outputting acceleration response on the right side, and outputting a vibration transmission characteristic curve; comparing the energy band structure with the transmission characteristic, and verifying the correctness of the position and the width of the band gap;
s4, changing the width and height of the local resonator and the longitudinal and transverse intervals of the local resonator, carrying out multiple times of simulation calculation on the original cell model of the ship hull plate frame superstructure, and determining the structural size of the ship hull plate frame superstructure by comprehensively considering factors including the light structure and the required forbidden band range;
s5, determining the relative position of a vibration source and a protection area, and additionally arranging local resonators with the structural size and the interval determined in the S4 on a hull plate frame structure in the middle of the vibration source and the protection area to establish a hull plate frame superstructure model with the actual size;
and S6, applying acceleration excitation at a vibration source, calculating an intrinsic displacement field of a superstructure model of the ship body plate frame in actual size, verifying the effectiveness of the arrangement mode of the local resonators, and finishing the design of the ship body plate frame structure.
In the above scheme, the frequency range of the vibration control is 0-500Hz.
In the above scheme, hull grillage structure include the deck with install in the vertical strengthening rib and the horizontal strengthening rib of deck bottom surface, vertical strengthening rib adopts the T section bar, horizontal strengthening rib adopts the L section bar.
In the above scheme, the lattice form of the slab frame superstructure is rectangular, and the local resonance is of a cuboid structure.
In the scheme, the longitudinal lattice constant a and the transverse lattice constant b of the grillage superstructure are both in the range of 300-800 mm; the width l and the height h of the local resonator are both in the range of 0.15a-0.35 a; the longitudinal interval m and the lateral interval n of the local resonators satisfy m = a, n = b, respectively.
In the scheme, the local resonator and the hull plate frame are made of marine steel.
In the scheme, COMSOL Multiphysics software is adopted to respectively establish a ship body plate frame superstructure primitive cell model and a ship body plate frame superstructure limited period model in the step S2, wherein the local resonator adopts solid units for modeling, and the ship body plate frame structure adopts shell units for modeling; carrying out mesh division on the shell unit by adopting a free triangular mesh, and dividing the mesh on the entity unit in a sweeping mode; adding material properties, including Young's modulus, poisson's ratio and density, to the solid unit and the shell unit respectively; and adding multi-physical field coupling to realize solid-shell connection.
The invention has the beneficial effects that:
1. the invention provides a design method of a plate frame superstructure, which verifies the correctness of the band gap position and the width of a ship body plate frame superstructure by establishing two models of the ship body plate frame superstructure and calculating the energy band structure and the transmission characteristic, and realizes effective isolation of low-frequency and medium-frequency vibration noise below 500Hz of ship mechanical equipment by introducing a local resonator. The vibration reduction in a specific frequency range can be realized by designing the size and the interval of the local area resonators, and the vibration reduction effect is improved.
2. The local resonator is of a cuboid structure, is simple in structure, is directly attached to the hull plate frame structure, and is convenient to process. The local resonator adopts the material with the same structure as the hull plate frame, and the integral forming can be realized through actual processing. The local resonator is attached to the same side of the cross area of the T-shaped section and the L-shaped section of the hull plate frame structure, and the original structure is not changed, so that the strength, rigidity, stability and reliability of the ship hull plate frame structure are ensured, and the installation of original equipment is not influenced.
Drawings
The invention will be further described with reference to the accompanying drawings and examples, in which:
FIG. 1 is a schematic structural diagram of a slab-rack superstructure in an embodiment of the invention (taking a 6 × 3 finite-period array structure as an example);
FIG. 2 is a schematic diagram of a cell structure of a latticed superstructure in an embodiment of the invention;
fig. 3 (a) is a band structure diagram of a hull plate frame superstructure primitive cell model in an embodiment of the invention;
FIG. 3 (b) is a transmission characteristic curve diagram of a finite-period model of a ship hull grillage superstructure in an embodiment of the invention;
FIG. 4 is a schematic representation of a superstructure of two types of real-size hull plating in an embodiment of the invention;
fig. 5 is the intrinsic displacement field for the two types of real ship size hull plate frame superstructures shown in fig. 4.
In the figure: 10. a hull plate frame structure; 11. a deck; 12. longitudinal reinforcing ribs; 13. transverse reinforcing ribs; 20. A local area resonator; 30. and (4) mechanical equipment.
Detailed Description
For a more clear understanding of the technical features, objects and effects of the present invention, embodiments of the present invention will now be described in detail with reference to the accompanying drawings.
The invention provides a method for designing a grillage superstructure suitable for low-frequency vibration isolation of ship mechanical equipment, which is used for carrying out vibration isolation design on a grillage structure of the ship mechanical equipment, wherein the grillage superstructure is shown in figure 1 and comprises a ship body grillage structure 10 and additional periodically arranged local resonators 20. The hull plate frame structure 10 comprises a deck 11, and a longitudinal reinforcing rib 12 and a transverse reinforcing rib 13 which are orthogonally distributed on the bottom surface of the deck in two directions, wherein the longitudinal reinforcing rib 12 is made of a T-shaped section, and the transverse reinforcing rib 13 is made of an L-shaped section. The bottom of the local resonance 20 is connected to the vessel deck 11. The slab-rack superstructure has a bending band gap in the low frequency range below 500Hz, which effectively isolates the further transmission of vibrations of mechanical device 30 to surrounding structures.
The invention relates to a grillage superstructure design method suitable for low-frequency vibration isolation of marine mechanical equipment, which comprises the following steps of:
s1, analyzing a vibration excitation source of typical mechanical equipment of a ship, and determining a required vibration isolation frequency range.
S2, aiming at the hull plate frame structure, considering the continuity of the model, arranging local resonators at intervals in the crossed area of the longitudinal reinforcing ribs and the transverse reinforcing ribs; and respectively establishing a ship hull grillage superstructure primitive cell model and a ship hull grillage superstructure finite period model.
In this embodiment, a ship hull plate-frame superstructure primitive cell model (as shown in fig. 2) and a ship hull plate-frame superstructure finite period model (as shown in fig. 1) are respectively established by using COMSOL Multiphysics software, and the ship hull plate-frame superstructure finite period model is composed of 6 × 3 ship hull plate-frame superstructure primitive cell models. The local resonator adopts solid units for modeling, and the hull plate frame structure adopts shell units for modeling; carrying out mesh division on the shell unit by adopting a free triangular mesh, and dividing the mesh on the entity unit in a sweeping mode; adding material properties, including Young's modulus, poisson's ratio and density, to the solid unit and the shell unit respectively; and adding multi-physical field coupling to realize solid-shell connection.
The longitudinal lattice constant of the grillage superstructure is a, the transverse lattice constant is b, the deck thickness is e, the width and height of the local resonator and the longitudinal and transverse intervals are l, h, m and n respectively, the length, the spacing, the height, the width, the web thickness and the wing plate thickness of the T-shaped section are a respectively 1 、l 1 、H、B、t 1 And t 2 The length, the interval, the edge width and the thickness of the L-shaped section are respectively b 1 、l 2 C and d. Specific structural parameters are as follows: a =600mm; b =500mm; e =6mm; l =100mm; h =100mm; m =600mm; n =500mm; a is 1 ＝600mm；l 1 ＝250mm；H＝50mm；B＝50mm；t 1 ＝5mm；t 2 ＝7mm；b 1 ＝500mm；l 2 =300mm; c =30mm; d =3mm. Material parameters: low carbon steel (density 7800 kg/m) 3 (ii) a Elastic dieQuantity 2X 10 11 Pa; poisson ratio 0.3).
S3, applying Floquet periodic boundary conditions in the X direction and the y direction of the original cell model of the ship hull plate frame superstructure, performing parameter scanning along wave vectors in the gamma-X-M-gamma direction, solving eigenmodes and eigenfrequencies of the structure under each wave vector, and obtaining an energy band structure of the ship hull plate frame superstructure by taking the wave vector direction as a horizontal coordinate and the eigenfrequencies as a vertical coordinate; applying acceleration excitation to simulate vibration source vibration on the left side of a ship hull plate frame superstructure finite period model, outputting acceleration response on the right side, and outputting a vibration transmission characteristic curve; and comparing the energy band structure with the transmission characteristic to verify the correctness of the position and the width of the band gap.
In this embodiment, as can be seen from the cell band structure diagram in fig. 3 (a), the grillage superstructure protocell has a complete band gap in the frequency range of 0-500Hz, and the band gap is between 205-285 Hz; on the other hand, as can be seen from the transmission characteristic curve of the finite period structure in fig. 3 (b), the grillage superstructure has a significant damping characteristic for bending vibration in the frequency range of 205-285Hz, and the bending vibration band gap width is 80Hz, so that low-frequency band and wide-frequency band vibration and noise reduction can be well realized. The band structure is well matched with the transmission characteristic band gap position and width.
And S4, changing the width and height of the local resonator and the longitudinal and transverse intervals of the local resonator, carrying out multiple times of simulation calculation on the primitive cell model according to the steps S2-S3, and determining the structural size of the ship body slab superstructure by comprehensively considering factors including the light structure and the required forbidden band range.
And S5, determining the relative position of the vibration source and the protection area, and additionally arranging local resonators with the structural size and the interval determined in the S4 on the hull plate frame structure in the middle of the vibration source and the protection area to establish a hull plate frame superstructure model with the actual size.
And S6, applying acceleration excitation at a vibration source, calculating an intrinsic displacement field of a superstructure model of the ship body plate frame in actual size, verifying the effectiveness of the arrangement mode of the local resonators, and finishing the design of the ship body plate frame structure.
Taking two types of local area resonator arrangement modes as shown in fig. 4 as an example, a ship hull plate frame superstructure model with actual size is established. Acceleration excitation is applied at the vibration source (i.e. at A), acceleration response is output in the protection area (i.e. at B), and two types of ship hull plate frame superstructure intrinsic displacement fields are output, as shown in figure 5. In the type I, a 6 multiplied by 4 local resonator is placed in the middle of a hull plate frame structure with a real ship size, excitation acceleration is applied to the left end of the plate frame structure to simulate excitation generated by ship mechanical equipment, and a protection area is located at the right end of the plate frame structure. Fig. 5 (a) and (b) show displacement fields with internal and external frequencies of band gap corresponding to type I, and corresponding frequencies are 229Hz and 305Hz respectively. As can be seen from fig. 5 (a), (b), when the excitation frequency of the excitation source is within the band gap range (f =229 Hz), the slab superstructure can effectively suppress the vibration near the excitation source, and prevent the excitation source from propagating to the protection area. When the excitation frequency of the excitation source is outside the band gap range (f =305 Hz), the elastic wave can smoothly propagate from the excitation source to the protection region. In type II, the local resonators are 3 x 4 local resonators placed at the two ends of the middle part, excitation acceleration is applied to the middle part of the plate frame structure to simulate the excitation generated by ship power equipment, and the protection areas are located at the two ends of the plate frame structure. As can also be seen from fig. 5 (c), (d), when the excitation frequency of the excitation source is within the band gap range (f =263 Hz), the slab-frame superstructure can effectively suppress the vibration near the excitation source; when the excitation frequency of the excitation source is outside the band gap range (f =403 Hz), the elastic wave can smoothly propagate from the excitation source to the protection region.
While the present invention has been described with reference to the embodiments shown in the drawings, the present invention is not limited to the embodiments, which are illustrative and not restrictive, and it will be apparent to those skilled in the art that various changes and modifications can be made therein without departing from the spirit and scope of the invention as defined in the appended claims.

Claims (7)

1. The method for designing the grillage superstructure suitable for low-frequency vibration isolation of ship mechanical equipment comprises a ship hull grillage structure and additional periodically-arranged local area resonators, and is characterized by comprising the following steps of:
s1, analyzing a vibration excitation source of typical mechanical equipment of a ship, and determining a required vibration isolation frequency range;
s2, aiming at the hull plate frame structure, considering the continuity of the model, arranging local resonators at intervals in the crossed area of the longitudinal reinforcing ribs and the transverse reinforcing ribs; respectively establishing a hull plate frame superstructure primitive cell model and a hull plate frame superstructure finite period model;
s3, floquet periodic boundary conditions are applied in the X direction and the y direction of the original cell model of the ship hull plate frame superstructure, parameter scanning is carried out along wave vectors in the gamma-X-M-gamma direction, the eigenmode and the eigenfrequency of the structure under each wave vector are solved, and the energy band structure of the ship hull plate frame superstructure is obtained by taking the wave vector direction as the abscissa and the eigenfrequency as the ordinate; applying acceleration excitation to simulate vibration source vibration on the left side of a ship hull plate frame superstructure finite period model, outputting acceleration response on the right side, and outputting a vibration transmission characteristic curve; comparing the energy band structure with the transmission characteristic, and verifying the correctness of the position and the width of the band gap;
s4, changing the width and height of the local resonator and the longitudinal and transverse intervals of the local resonator, carrying out multiple simulation calculation on the primitive cell model of the hull plate frame superstructure, and comprehensively considering factors including the light structure and the required forbidden band range to determine the structural size of the hull plate frame superstructure;
s5, determining the relative position of a vibration source and a protection area, and additionally arranging local resonators with the structural size and the interval determined in the S4 on a hull plate frame structure in the middle of the vibration source and the protection area to establish a hull plate frame superstructure model with the actual size;
and S6, applying acceleration excitation at a vibration source, calculating an intrinsic displacement field of a superstructure model of the ship body plate frame in actual size, verifying the effectiveness of the arrangement mode of the local resonators, and finishing the design of the ship body plate frame structure.
2. The method for designing a grillage superstructure suitable for low-frequency vibration isolation of marine mechanical equipment according to claim 1, wherein the frequency range of vibration control is 0-500Hz.
3. The method for designing the grillage superstructure suitable for low-frequency vibration isolation of marine mechanical equipment according to claim 1, wherein the hull grillage structure comprises a deck and longitudinal reinforcing ribs and transverse reinforcing ribs which are arranged on the bottom surface of the deck, the longitudinal reinforcing ribs are T-shaped bars, and the transverse reinforcing ribs are L-shaped bars.
4. The method for designing the grillage superstructure suitable for low-frequency vibration isolation of marine mechanical equipment as claimed in claim 1, wherein the lattice form of the grillage superstructure is rectangular, and the local resonance is of a rectangular parallelepiped structure.
5. The method for designing the grillage superstructure suitable for low-frequency vibration isolation of marine mechanical equipment as claimed in claim 4, wherein a longitudinal lattice constant a and a transverse lattice constant b of the grillage superstructure are both in a range of 300-800 mm; the width l and the height h of the local resonator are both in the range of 0.15a-0.35 a; the longitudinal interval m and the lateral interval n of the local resonators satisfy m = a, n = b, respectively.
6. The method for designing the grillage superstructure suitable for low-frequency vibration isolation of marine mechanical equipment according to claim 1, wherein the local resonator and the hull grillage structure are made of marine steel.
7. The method for designing the plate frame superstructure suitable for the low-frequency vibration isolation of the marine mechanical equipment as claimed in claim 1, wherein COMSOL Multiphysics software is adopted in the step S2 to respectively establish a ship plate frame superstructure primitive cell model and a ship plate frame superstructure finite period model, wherein a local area resonator is modeled by using solid units, and a ship plate frame structure is modeled by using shell units; carrying out mesh division on the shell unit by adopting a free triangular mesh, and dividing the mesh on the entity unit in a sweeping mode; adding material properties, including Young's modulus, poisson's ratio and density, to the solid unit and the shell unit respectively; and adding multi-physical field coupling to realize solid-shell connection.
CN202210972973.6A 2022-08-15 2022-08-15 Grillage superstructure design method suitable for low-frequency vibration isolation of ship mechanical equipment Pending CN115408833A (en)

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