CN102663212A - Optimized design method for ship anchoring machine seat - Google Patents
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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, effects such as windlass plays and weighs anchor, casts anchor, mooring and band cable, the accommodation is constant to keeping for its reliability properties, brake hard boats and ships and make ship safety play decisive role by leaving wharf.In carrying out windlass new product development process; Most of producers use classical experience formula to design anchor winch parts; Can only adopt higher safety coefficient to ensure its security; Make that gypsy wheel size and weight are increasing, theoretical load-bearing capacity exists than big-difference with actual load-bearing capacity, and this method has that narrow application range, analysis precision are low, to obtain quantity of information little and calculate the too conservative defective such as structure heaviness that causes.If to the anchor winch of complex structure, new material or new technology, this method then error is very big.
Along with value theory and development of computer, 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 2007 the 36th the 2nd phases of volume of ship maritime works journey has been announced the method that adopts finite element method analysis windlass support; Afterwards, write by square development, Zhang Lianda, " finite element analysis of windlass pedestal " paper of 2008 the 1st phases of Guangdong shipbuilding 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 present boats and ships windlass support finite element is earlier entity to be carried out three-dimensional modeling; Further it is carried out the design of real working condition then, at last its structure is optimized, under the situation that satisfies function and safety; Reduce manufacturing cost, and shorten the design cycle.Yet, relevant confirm that at conceptual phase support optimum topology structure and the designing technique of confirming to satisfy the lightest boats and ships windlass stand structure of the weight of certain intensity, rigidity at detailed design phase afterwards do not appear in the newspapers.
Summary of the invention
The objective of the invention is the defective that exists to 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 scheme that the present invention adopts is may further comprise the steps:
The first step: according to the basic design parameters of windlass, confirm support physical dimension, set up said support three-dimensional model;
Second step: set up the 3D solid finite element model and the topological optimization model of said support, carry out topology optimization design under the holding load operating mode;
The 3rd step:, confirm the preferred version of at least a support according to the topological optimization result;
The 4th step: use shell unit to set up the simplification finite element model of said preferred version, carry out dimensionally-optimised design under the holding load operating mode, confirm optimum stand structure;
The 5th step: said optimum stand structure is carried out structural design, confirm final support model, promptly be designed to the actual entities stand structure to said optimum shell unit stand structure.
The unit of described 3D solid finite element model adopts hexahedron and minority pentahedron, and pentahedron quantity is less than 3% of the unit sum, and thickness direction is provided with 6 layers at least; The upper part of the frame of said 3D solid finite element model adopts the constraint of multiple spot motion coupling unit, and on multiple spot motion coupling unit independent point, applies the holding load operating loading, and all nodes of constraint 3D solid finite element model bottom surface.
In the described topological optimization model design variable be said 3D solid finite element the pseudo-density in unit, be constrained to volume fraction less than 0.3, target is that the structure flexibility is minimum.
In said topological optimization result, remove the pseudo-density 0.3 in unit with interior part,, confirm preferred version according to the remaining best Path of Force Transfer of partly finding out support;
Said shell unit is quadrilateral and minority triangular element; Triangular element quantity is less than 3% of the unit sum; The constraint of multiple spot motion coupling unit is adopted on said shell unit model top; And on multiple spot motion coupling unit independent point, apply the holding load operating loading, and all nodes of constraint shell unit finite element model bottom surface.
Design variable is said thickness of shell and is that volume is minimum for discrete design variable, constraint comprise thickness, displacement and stress constraint 3 parts, target in the said dimensionally-optimised design.
The present invention can confirm support optimum topology structure and the lightest stand structure of weight of confirming to satisfy certain intensity, rigidity afterwards at detailed design phase at conceptual phase, promptly can design topological structure the best, windlass support that weight is the lightest.
Description of drawings
Fig. 1 is a process flow diagram of the present invention;
Fig. 2 is the synoptic diagram of windlass support geometric model;
Fig. 3 is the synoptic diagram of windlass support grid finite element model;
Fig. 4 is a windlass support topological optimization synoptic diagram as a result;
Fig. 5 a～5c is the synoptic diagram of windlass support according to the shell unit finite element model of the selected scheme of topological optimization;
Fig. 6 is the synoptic diagram of the stand structure three-dimensional model of windlass support optimal case;
Among the figure: the X axle is the support length direction; The Z axle is the support Width; The Y axle is the support short transverse.
Embodiment
Referring to Fig. 1, according to the basic design parameters of boats and ships windlass, confirm support physical dimension earlier, set up the three-dimensional model of support.
To three-dimensional model, set up 3D solid finite element model and topological optimization model, confirm the preferred version of support.Wherein, the unit of 3D solid finite element model adopts hexahedron and minority pentahedron, and pentahedron quantity is less than 3% of the unit sum, and thickness direction is provided with 6 layers at least; The upper part of the frame of 3D solid finite element model adopts the constraint of multiple spot motion coupling unit; And on multiple spot motion coupling unit independent point, apply the holding load operating loading; And all nodes of constraint 3D solid finite element model bottom surface; Carry out topology optimization design under the holding load operating mode, set up the topological optimization model, in the topological optimization model design variable be the 3D solid finite element the pseudo-density in unit, be constrained to volume fraction less than 0.3, target is that the structure flexibility is minimum; According to the topological optimization result; In the topological optimization result, remove the pseudo-density 0.3 in unit with interior part,, confirm the preferred version of at least a support according to the remaining best Path of Force Transfer of partly finding out support.
Use shell unit to set up the simplification finite element model of this preferred version; Carry out dimensionally-optimised design under the holding load operating mode; Confirm optimum stand structure; This optimum stand structure is carried out structural design, confirm final support model, promptly be designed to the actual entities stand structure to optimum shell unit stand structure.Wherein, Shell unit is quadrilateral and minority triangular element; Triangular element quantity is less than 3% of the unit sum; The constraint of multiple spot motion coupling unit is adopted on shell unit model top, and on multiple spot motion coupling unit independent point, applies the holding load operating loading, and all nodes of constraint shell unit finite element model bottom surface; Carry out 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 in the dimensionally-optimised design.
1 embodiment of the present invention below is provided.
Embodiment
The basic design parameters of boats and ships windlass is: anchor chain diameter phi 44 (AM3); Operating load F
C=92kN; The 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; The reel operating load is 60kN; Rope capacity is 180m * φ 48mm (single); Mooring speed is 15 m/min; Negative reel pulling force is 30KN; The oil motor model is NHM31-4000B (just deciding Ningbo Ying Temu); Discharge capacity q
0=4153ml/r.The pumping plant parameter is: oil pump model 160SCY14-1B; Motor model Y225S-4-H-B3,37KW/380V, 50Hz.According to step shown in Figure 1 this windlass support is optimized design below.
The first step: confirm that through the calculating of Machine Design this support physical dimension parameter is according to above-mentioned windlass parameter: long 1000mm, high 905mm, wide 170mm, the 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 is as shown in Figure 2, comprises the top end cap that is connected with main shaft, the bottom that is connected with deck in ship structure and transitional region between the two.Under the holding load operating mode, the load that this windlass support is born is 345.5kN, and direction is vertical with the Z axle, and respectively becomes 45 ° with X axle and Y axle
Second step: set up the 3D solid finite element model (like Fig. 3) and the topological optimization model thereof of support shown in Figure 2, carry out topology optimization design under the holding load operating mode.Among Fig. 2,1 is end cap, and 2 is transitional region, and 3 is base plate.The support 3D solid finite element model of being set up is reasonably divided for 122145 hexahedrons and 2652 pentahedrons, and thickness direction is that Z-direction is 17 layers, totally 133903 nodes, and the definition elastic modulus is 206GPa, Poisson ratio is 0.3.Adopt multiple spot motion coupling unit (MPC) constraint at upper part of the frame; And the power that on multiple spot motion coupling unit independent point, imposes restriction; The size of making a concerted effort that is Y direction and X axle positive dirction all is 345.5kN, and all degree of freedom of all nodes of constraint 3D solid finite element model bottom surface; Set up support topological optimization model on this basis and on the basis of Fig. 3, be provided with, design variable is the pseudo-density 0.3 in the unit of 3D solid finite element model, be constrained to volume fraction less than 0.3 and at Z to being symmetry, target is that the structure flexibility is minimum; Carry out topological optimization and find the solution the motion FEM calculation, in Optimization result, remove the pseudo-density 0.3 in unit with interior part be integral material 30% in.
In the 3rd step, remaining part has demonstrated the best Path of Force Transfer of support, and the result is as shown in Figure 4.Then can remove according to the stressed on one side big remainder of Fig. 4 result; Only need add in a stressed big side forces it can bear so big load; Fig. 5 a has cut down the integral thickness of middle plate, but has added a reinforcement in a stressed big side, and Fig. 5 b removes some materials of below according to the result; Fig. 5 c has added reinforcement and the stressed less part material of can removing of opposite side in a stressed side, 3 kinds of schemes that show among Fig. 5 a-Fig. 5 c all be Z to symmetrical structure.
In the 4th step, use shell unit to set up the simplification finite element model of 3 kinds of preferred versions (Fig. 5 a～5c), face in the extraction; Carrying out two-dimensional grid then divides it; Model comprises zone of transition and base plate, and the definition elastic modulus is 206GPa, and Poisson ratio is 0.3; Concrete model information is as shown in table 1 below; Adopt multiple spot motion coupling unit (MPC) constraint on the top of the support of 3 kinds of preferred versions, and on multiple spot motion coupling unit independent point, apply 345.5kN, direction is vertical with the Z axle and respectively become 45 ° power with the X axle with the Y axle, retrains all degree of freedom of 3 kinds of all nodes of preferred version bottom surface in addition; Set up dimensionally-optimised model on this basis: design variable is middle plate, side plate and the reinforcement thickness in the zone of transition; They are the discrete design variable, and with the variable quantity variation of 1mm, optimizing the zone is side plate, middle plate and reinforcement; Specifying information sees the following form 2, and is optimized and finds the solution; Final optimization pass result and corresponding mechanical property parameters are respectively 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 scheme weight is the lightest shown in Fig. 5 a; Therefore, the final scheme of confirming is a scheme shown in Fig. 5 a, and it had both come from the topological optimization structure; Satisfy intensity, rigidity requirement simultaneously, this structure is final optimizing structure.
Below be the information of each model; Data all are in utilization Hyper works design process, to obtain in the table; The plate of X-direction is middle plate in 3 kinds of schemes among Fig. 5 a～5c, in passing plate and with middle plate be the plane of symmetry be reinforcement, what surround that both sides extend at the Z axle is side plate.Quadrilateral units and triangular element all are 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 |
| The quadrilateral units sum | 14845 | 13687 | 12244 |
| The triangular element sum | 171 | 183 | 200 |
| The 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 |
| Reinforcement thickness (mm) | 10 | 10 | 40 |
| Side plate thickness (mm) | 10 | 10 | 10 |
The mechanical property contrast of the dimensionally-optimised back 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, carry out three-dimensional design according to table 3 pair said optimum stand structure (scheme shown in Fig. 5 a), confirm that final support model institute is shown in Figure 6.
Claims (6)
1. a boats and ships windlass support Optimization Design is characterized in that comprising the steps:
1) according to the basic design parameters of windlass, confirm support physical dimension, set up the support three-dimensional model;
2) set up the 3D solid finite element model and the topological optimization model of support, carry out topology optimization design under the holding load operating mode;
3), confirm the preferred version of at least a support according to the topological optimization result;
4) use shell unit to set up the simplification finite element model of said preferred version, carry out dimensionally-optimised design under the holding load operating mode, confirm optimum stand structure;
5) said optimum stand structure is carried out structural design, confirm final support model.
2. boats and ships windlass support Optimization Design according to claim 1 is characterized in that: the unit of described 3D solid finite element model adopts hexahedron and minority pentahedron, and pentahedron quantity is less than 3% of the unit sum, and thickness direction is provided with 6 layers at least; The upper part of the frame of said 3D solid finite element model adopts the constraint of multiple spot motion coupling unit, and on multiple spot motion coupling unit independent point, applies the holding load operating loading, and all nodes of constraint 3D solid finite element model bottom surface.
3. boats and ships windlass support Optimization Design according to claim 1 is characterized in that: in the described topological optimization model design variable be said 3D solid finite element the pseudo-density in unit, be constrained to volume fraction less than 0.3, target is that the structure flexibility is minimum.
4. boats and ships windlass support Optimization Design according to claim 1 is characterized in that: in said topological optimization result, remove the pseudo-density 0.3 in unit with interior part, according to the remaining best Path of Force Transfer of partly finding out support, confirm preferred version.
5. boats and ships windlass support Optimization Design according to claim 1; It is characterized in that: said shell unit is quadrilateral and minority triangular element; Triangular element quantity is less than 3% of the unit sum; The constraint of multiple spot motion coupling unit is adopted on said shell unit model top, and on multiple spot motion coupling unit independent point, applies the holding load operating loading, and all nodes of constraint shell unit finite element model bottom surface.
6. boats and ships windlass support Optimization Design according to claim 1 is characterized in that: design variable is said thickness of shell and is that volume is minimum for discrete design variable, constraint comprise thickness, displacement and stress constraint 3 parts, target in the said dimensionally-optimised design.
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| CN105718621A (en) * | 2014-12-18 | 2016-06-29 | 中国航空工业集团公司沈阳发动机设计研究所 | Optimal design method for external bracket of engine |
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| CN113722824A (en) * | 2021-08-30 | 2021-11-30 | 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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| 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 |
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| US10471913B2 (en) | 2015-09-30 | 2019-11-12 | Sabic Global Technologies B.V. | Load-bearing parts with networks of interconnecting branches and methods of making the same |
| 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 |
| CN110532686A (en) * | 2019-08-29 | 2019-12-03 | 中国海洋大学 | A kind of equipment On The Offshore Platform installation pedestal structural optimization method |
| CN110532686B (en) * | 2019-08-29 | 2022-07-05 | 中国海洋大学 | Structure optimization method for installation base of ocean platform equipment |
| CN110704976A (en) * | 2019-09-30 | 2020-01-17 | 西北工业大学 | Novel construction method of high-performance pentahedron six-node body shell unit |
| CN111709094A (en) * | 2020-07-13 | 2020-09-25 | 江苏科技大学 | Method for optimizing base structure of anchor and mooring machine |
| CN111709094B (en) * | 2020-07-13 | 2024-01-30 | 江苏科技大学 | Base structure optimization method of anchor windlass |
| CN113722824A (en) * | 2021-08-30 | 2021-11-30 | 江南造船(集团)有限责任公司 | Ship plate structure simplification method and device suitable for finite element analysis |
| 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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