CN102663212B - Optimized design method for ship anchoring machine seat - Google Patents
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- CN102663212B CN102663212B CN201210140087.3A CN201210140087A CN102663212B CN 102663212 B CN102663212 B CN 102663212B CN 201210140087 A CN201210140087 A CN 201210140087A CN 102663212 B CN102663212 B CN 102663212B
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Abstract
The invention discloses an optimized design method for a ship anchoring machine seat. The method comprises the following steps of: determining the appearance and the size of the machine seat according to basic design parameters of an anchoring machine, and constructing a three-dimensional model of the machine seat; constructing a three-dimensional entity finite element model and a topology optimization model of the machine seat, and performing topology optimization design under working condition of supporting a load; determining at least one preferable scheme of the machine seat according to a topology optimization result; constructing a simplified finite element model of the preferable scheme by using a shell unit, performing size optimization design under the working condition of supporting the load, and determining an optimal machine seat structure; and finally performing structural design on the optimal machine seat structure, and determining a final machine seat model, namely the optimal shell unit machine seat structure is an actual entity machine seat structure. The optimal topological structure of the machine seat can be determined in a concept design stage, and a machine seat structure which meets certain intensity and rigidity and is the lightest can be determined in the subsequent detail design stage.
Description
Technical field
The invention belongs to mechanical design field, relate to a kind of boats and ships windlass method for designing, relate in particular to a kind of Optimization Design of boats and ships windlass support.
Background technology
As modern ships deck machinery important component part, the effects such as windlass plays and weighs anchor, casts anchor, mooring and band cable, accommodation is constant to keeping for its reliability properties, brake hard boats and ships and make ship play decisive role by leaving wharf safely.In carrying out windlass New Product Development Process, most of producers design anchor winch parts by classical experimental formula, can only adopt higher safety coefficient to ensure its security, make gypsy wheel size and weight increasing, there is larger difference in theoretical load-bearing capacity and actual load-bearing capacity, this method has narrow application range, analysis precision is low, obtaining information amount is little and calculate the too conservative defects such as structure heaviness that cause.If for the anchor winch of complex structure, new material or new technology, this method error is very large.
Along with the development of value theory and computer technology, finite element method has been widely used in the design analysis of windlass.By Hu Fucai, Zhou Yong, on the sunny side, Yang Jianguo writes, " finite element analysis of windlass support and experimental study " paper of ship sea engineering the 36th the 2nd phase of volume in 2007 has been announced the method that adopts finite element method analysis windlass support; Afterwards, by square development, Zhang Lianda, write, " finite element analysis of windlass pedestal " paper of Guangdong shipbuilding the 1st phase in 2008 has also been announced the technology that adopts finite element software ANSYS software to carry out the intensive analysis of windlass support.
The method for designing of current boats and ships windlass support finite element is first entity to be carried out to three-dimensional modeling, then further it is carried out the design of real working condition, finally its structure is optimized, in the situation that meeting function and safety, reduce manufacturing cost, and shorten the design cycle.Yet, relevant at conceptual phase, determine support optimum topology structure and at detailed design phase, determine that the designing technique that meets the boats and ships windlass stand structure that the weight of some strength, rigidity is the lightest has no report afterwards.
Summary of the invention
The object of the invention is the defect existing for prior art and the boats and ships windlass support that a kind of scope of application is wide, precision is high Optimization Design is provided.
The technical solution used in the present invention is to comprise the following steps:
The first step: according to the basic design parameters of windlass, determine support physical dimension, set up described support three-dimensional model;
Second step: set up solid finite element model and the Topological optimization model of described support, carry out topology optimization design under holding load operating mode;
The 3rd step: according to topological optimization result, determine the preferred version of at least one support;
The 4th step: use shell unit to set up the simplification finite element model of described preferred version, carry out dimensionally-optimised design under holding load operating mode, determine optimum stand structure;
The 5th step: described optimum stand structure is carried out to structural design, determine final support model, described optimum shell unit stand structure is designed to actual entities stand structure.
The unit of described solid finite element model adopts hexahedron and minority pentahedron, and pentahedron quantity is less than 3% of unit sum, and thickness direction at least arranges 6 layers; The upper part of the frame of described solid finite element model adopts the constraint of multiple spot sports coupling unit, and applies holding load operating loading in multiple spot sports coupling unit independent point, and all nodes in constraint solid finite element model bottom surface.
The pseudo-density in unit that in described Topological optimization model, design variable is described solid finite element, be constrained to that volume fraction is less than 0.3, target is that structure flexibility is minimum.
In described topological optimization result, the pseudo-density 0.3 of removal unit, with interior part, is found out the best Path of Force Transfer of support according to remaining part, determines preferred version;
Described shell unit is quadrilateral and minority triangular element, triangular element quantity is less than 3% of unit sum, described shell unit model top adopts the constraint of multiple spot sports coupling unit, and apply holding load operating loading in multiple spot sports coupling unit independent point, and all nodes in constraint shell unit finite element model bottom surface.
In described dimensionally-optimised design, design variable is described thickness of shell and is that volume is minimum for discrete design variable, constraint comprise thickness, displacement and stress constraint 3 parts, target.
The present invention can determine support optimum topology structure and at detailed design phase, determine the lightest stand structure of weight meet some strength, rigidity afterwards at conceptual phase, can design topological structure the best, windlass support that weight is the lightest.
Accompanying drawing explanation
Fig. 1 is process flow diagram of the present invention;
Fig. 2 is the schematic diagram of windlass support geometric model;
Fig. 3 is the schematic diagram of windlass support grid finite element model;
Fig. 4 is windlass support topological optimization result schematic diagram;
Fig. 5 a～5c is that windlass support is according to the schematic diagram of the shell unit finite element model of the selected scheme of topological optimization;
Fig. 6 is the schematic diagram of the stand structure three-dimensional model of windlass support optimal case;
In figure: X-axis is support length direction; Z axis is support Width; Y-axis is support short transverse.
Embodiment
Referring to Fig. 1, first according to the basic design parameters of boats and ships windlass, determine support physical dimension, set up the three-dimensional model of support.
For three-dimensional model, set up solid finite element model and Topological optimization model, determine the preferred version of support.Wherein, the unit of solid finite element model adopts hexahedron and minority pentahedron, and pentahedron quantity is less than 3% of unit sum, and thickness direction at least arranges 6 layers, the upper part of the frame of solid finite element model adopts the constraint of multiple spot sports coupling unit, and apply holding load operating loading in multiple spot sports coupling unit independent point, and all nodes in constraint solid finite element model bottom surface, carry out topology optimization design under holding load operating mode, set up Topological optimization model, the pseudo-density in unit that in Topological optimization model, design variable is solid finite element, be constrained to volume fraction and be less than 0.3, target is that structure flexibility is minimum, according to topological optimization result, in topological optimization result, the pseudo-density 0.3 of removal unit is with interior part, according to remaining part, find out the best Path of Force Transfer of support, determine the preferred version of at least one support.
Use shell unit to set up the simplification finite element model of this preferred version, carry out dimensionally-optimised design under holding load operating mode, determine optimum stand structure, this optimum stand structure is carried out to structural design, determine final support model, optimum shell unit stand structure is designed to actual entities stand structure.Wherein, shell unit is quadrilateral and minority triangular element, triangular element quantity is less than 3% of unit sum, shell unit model top adopts the constraint of multiple spot sports coupling unit, and apply holding load operating loading in multiple spot sports coupling unit independent point, and all nodes in constraint shell unit finite element model bottom surface, carry out dimensionally-optimised design, in dimensionally-optimised design, design variable is thickness of shell and is that volume is minimum for discrete design variable, constraint comprise thickness, displacement and stress constraint 3 parts, target.
1 embodiment of the present invention is below provided.
Embodiment
The basic design parameters of boats and ships windlass is: anchor chain diameter phi 44(AM3); Operating load F
c=92kN; Overload pulling force is 138kN; The speed of weighing anchor V
c>=9m/min; Teeth number of sprocket is 6; Sprocket wheel pitch diameter D=φ 704mm; Sprocket wheel calculated diameter D
0=φ 672mm; Holding load is 691kN; Reel operating load is 60kN; Rope capacity is that 180m * φ 48mm(is single); Mooring speed is 15 m/min; Negative reel pulling force is 30KN; Oil motor model is NHM31-4000B(Chu Ding Ningbo Ying Temu); Discharge capacity q
0=4153ml/r.Pumping plant parameter is: oil pump model 160SCY14-1B; Motor model Y225S-4-H-B3,37KW/380V, 50Hz.According to the step shown in Fig. 1, this windlass support is optimized to design below.
The first step: this support physical dimension parameter of calculative determination according to above-mentioned windlass parameter by Machine Design is: long 1000mm, high 905mm, wide 170mm, side plate gradient is 11 °, and the elastic modulus of material is 206GPa, and Poisson ratio is 0.3, and density is 7900Kg/m
3, general structure as shown in Figure 2, comprises the top end cap being connected with main shaft, the bottom being connected with deck in ship structure and transitional region between the two.Under holding load operating mode, the load that this windlass support bears is 345.5kN, and direction is vertical with Z axis, and each is at 45 ° with X-axis and Y-axis
Second step: set up solid finite element model (as Fig. 3) and the Topological optimization model thereof of support shown in Fig. 2, carry out topology optimization design under holding load operating mode.In Fig. 2,1 is end cap, and 2 is transitional region, and 3 is base plate.The support solid finite element model of setting up is reasonably divided for 122145 hexahedrons and 2652 pentahedrons, and thickness direction is that Z-direction is 17 layers, totally 133903 nodes, and definition elastic modulus is 206GPa, Poisson ratio is 0.3.At upper part of the frame, adopt multiple spot sports coupling unit (MPC) constraint, and the power that imposes restriction in multiple spot sports coupling unit independent point, the size of making a concerted effort that is Y direction and X-axis positive dirction is all 345.5kN, and all degree of freedom of all nodes in constraint solid finite element model bottom surface; Set up on this basis support Topological optimization model and arrange on the basis of Fig. 3, design variable is the pseudo-density 0.3 in the unit of solid finite element model, be constrained to volume fraction be less than 0.3 and in Z-direction for symmetrical, target is that structure flexibility is minimum; Carry out topological optimization and solve motion FEM (finite element) calculation, in optimum results the pseudo-density 0.3 of removal unit with interior part be integral material 30% in.
The 3rd step, remaining partial display has gone out the best Path of Force Transfer of support, and result is as shown in Figure 4.According to the stressed larger remainder in Fig. 4 result one side, can remove, only need strengthen bearing so large load in a stressed large side, Fig. 5 a has cut down the integral thickness of middle plate, but added a reinforcement in a stressed large side, Fig. 5 b removes some materials of below according to result, Fig. 5 c a stressed side added reinforcement and opposite side stressed compared with I to remove part material, 3 kinds of schemes that show in Fig. 5 a-Fig. 5 c are all the symmetrical structures in Z-direction.
The 4th step, use shell unit to set up the simplification finite element model (Fig. 5 a～5c) of 3 kinds of preferred versions, face in extraction, then carrying out two-dimensional grid divides it, model comprises zone of transition and base plate, definition elastic modulus is 206GPa, Poisson ratio is 0.3, concrete model information is as shown in table 1 below, on the top of the support of 3 kinds of preferred versions, adopt multiple spot sports coupling unit (MPC) constraint, and apply 345.5kN in multiple spot sports coupling unit independent point, direction is vertical with Z axis, and with X-axis and each power at 45 ° of Y-axis, in addition retrain all degree of freedom of 3 kinds of all nodes in preferred version bottom surface, set up on this basis dimensionally-optimised model: design variable is middle plate, side plate and the Rib Thickness in zone of transition, they are discrete design variable, and with the variable quantity variation of 1mm, optimization region is side plate, middle plate and reinforcement, specifying information sees the following form 2, and carries out Optimization Solution, final optimization pass result and corresponding mechanical property parameters are respectively as shown in following table 3 and 4.According to table 4, the strength and stiffness of 3 kinds of schemes all meet the demands, and shown in Fig. 5 a, scheme weight is the lightest, therefore, final definite scheme is scheme shown in Fig. 5 a, and it had both come from topological optimization structure, meet intensity, rigidity requirement, this structure is final optimizing structure simultaneously.
Be below the information of each model, in table, data are all to obtain in using Hyper works design process, in 3 kinds of schemes in Fig. 5 a～5c, the plate of X-direction is middle plate, and what through middle plate the middle plate of take, be the plane of symmetry is reinforcement, and what surround that both sides extend at Z axis is side plate.Quadrilateral units and triangular element are all two-dimentional unit, and triangular element is normal strain unit, and the shape function of quadrilateral units to be hyperbolic curve internal strain state be changes.
The model information of 3 kinds of preferred versions of table 1
| ? | Scheme shown in Fig. 5 a | Scheme shown in Fig. 5 b | Scheme shown in Fig. 5 c |
| Quadrilateral units sum | 14845 | 13687 | 12244 |
| Triangular element sum | 171 | 183 | 200 |
| Node sum | 15118 | 14078 | 12607 |
The dimensionally-optimised model of 3 kinds of preferred versions of table 2
The dimensionally-optimised result of 3 kinds of preferred versions of table 3
| Scheme | Scheme shown in Fig. 5 a | Scheme shown in Fig. 5 b | Scheme shown in Fig. 5 c |
| Middle plate thickness (mm) | 15 | 20 | 15 |
| Rib Thickness (mm) | 10 | 10 | 40 |
| Side plate thickness (mm) | 10 | 10 | 10 |
The dimensionally-optimised rear mechanical property contrast of 3 kinds of preferred versions of table 4
| Scheme | Scheme shown in Fig. 5 a | Scheme shown in Fig. 5 b | Scheme shown in Fig. 5 c |
| Maximum displacement (mm) | 0.27 | 0.25 | 0.24 |
| Maximum stress (MPa) | 96.9 | 82.9 | 80.57 |
| General assembly (TW) (kg) | 178 | 201 | 182 |
The 5th step, carries out three-dimensional design according to table 3 pair described optimum stand structure (scheme shown in Fig. 5 a), determines shown in final support model Fig. 6.
Claims (5)
1. a boats and ships windlass support Optimization Design, comprises the following steps:
1) according to the basic design parameters of windlass, determine support physical dimension, set up support three-dimensional model;
2) set up solid finite element model and the Topological optimization model of support, carry out topology optimization design under holding load operating mode;
3), according to topological optimization result, determine the preferred version of at least one support;
4) use shell unit to set up the simplification finite element model of described preferred version, carry out dimensionally-optimised design under holding load operating mode, determine optimum stand structure;
5) described optimum stand structure is carried out to structural design, determines final support model,
It is characterized in that:
The unit of described solid finite element model adopts hexahedron and minority pentahedron, and pentahedron quantity is less than 3% of unit sum, and thickness direction at least arranges 6 layers; The upper part of the frame of described solid finite element model adopts the constraint of multiple spot sports coupling unit, and applies holding load operating loading in multiple spot sports coupling unit independent point, and all nodes in constraint solid finite element model bottom surface.
2. boats and ships windlass support Optimization Design according to claim 1, is characterized in that: the pseudo-density in unit that in described Topological optimization model, design variable is described solid finite element, be constrained to that volume fraction is less than 0.3, target is that structure flexibility is minimum.
3. boats and ships windlass support Optimization Design according to claim 1, is characterized in that: in described topological optimization result, the pseudo-density 0.3 of removal unit, with interior part, is found out the best Path of Force Transfer of support according to remaining part, determines preferred version.
4. boats and ships windlass support Optimization Design according to claim 1, it is characterized in that: described shell unit is quadrilateral and minority triangular element, triangular element quantity is less than 3% of unit sum, described shell unit model top adopts the constraint of multiple spot sports coupling unit, and apply holding load operating loading in multiple spot sports coupling unit independent point, and all nodes in constraint shell unit finite element model bottom surface.
5. boats and ships windlass support Optimization Design according to claim 1, is characterized in that: in described dimensionally-optimised design, design variable is described thickness and is discrete design variable, and constraint comprises thickness, displacement and stress constraint 3 parts, and target is that volume is minimum.
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| CN105718621B (en) * | 2014-12-18 | 2019-12-27 | 中国航空工业集团公司沈阳发动机设计研究所 | Engine external support optimization design method |
| CN105205254B (en) * | 2015-09-21 | 2018-07-03 | 江苏科技大学 | A kind of trough of belt takes out the optimum design method of shell mold plate |
| CN108349542A (en) | 2015-09-30 | 2018-07-31 | 沙特基础工业全球技术公司 | Load bearing component and its manufacturing method with interconnection branch mesh |
| CN105975734A (en) * | 2016-07-12 | 2016-09-28 | 中国航空工业集团公司沈阳发动机设计研究所 | Method for optimized design of external support of engine |
| CN110532686B (en) * | 2019-08-29 | 2022-07-05 | 中国海洋大学 | Structure optimization method for installation base of ocean platform equipment |
| CN110704976B (en) * | 2019-09-30 | 2020-09-01 | 西北工业大学 | Construction method of pentahedron six-node body shell unit for aerospace thin-wall shell modeling |
| CN111709094B (en) * | 2020-07-13 | 2024-01-30 | 江苏科技大学 | Base structure optimization method of anchor windlass |
| CN113722824B (en) * | 2021-08-30 | 2024-01-12 | 江南造船(集团)有限责任公司 | Ship plate structure simplification method and device suitable for finite element analysis |
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Application publication date: 20120912 Assignee: SHANGHAI ZHENHUA HEAVY INDUSTRY QIDONG MARINE ENGINEERING CO., LTD. Assignor: Jiangsu University of Science and Technology Contract record no.: 2015320000089 Denomination of invention: Optimized design method for ship anchoring machine seat Granted publication date: 20140115 License type: Exclusive License Record date: 20150320 |
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