CN112989571B - Stress optimization method for amplitude-variable oil cylinder of ultra-large pile driving ship - Google Patents
Stress optimization method for amplitude-variable oil cylinder of ultra-large pile driving ship Download PDFInfo
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Abstract
The invention discloses a stress optimization method of an amplitude variation oil cylinder of an oversized pile driving ship, which comprises the following steps: determining a design variable; inputting design variables into the Exce l software; determining an objective function: maximum pulling force and maximum pushing force of the oil cylinder; determining constraint conditions: under the rest state, the pile frame is restrained from interfering with the main deck by the rear included angle structure; the maximum installation length of the upper end of the piston rod of the oil cylinder when hinged at the second upper hinged point of the oil cylinder is restrained to be approximately equal to that of the upper end of the piston rod of the oil cylinder when hinged at the first upper hinged point of the oil cylinder; the minimum installation length of the upper end of the piston rod of the oil cylinder when hinged at the second upper hinged point of the oil cylinder is restrained to be approximately equal to the minimum installation length of the upper end of the piston rod of the oil cylinder when hinged at the first upper hinged point of the oil cylinder; restraining the structure of the oil cylinder; and inputting the objective function and the constraint condition into the Exce l software to calculate the stress of the oil cylinder. The invention can conveniently find the arrangement size of the pile frame and the amplitude variation oil cylinder when the amplitude variation oil cylinder is stressed better without software programming.
Description
Technical Field
The invention relates to a stress optimization method for an amplitude-variable oil cylinder of an ultra-large pile driving ship.
Background
The amplitude-variable oil cylinder is key equipment of the pile frame type piling ship, not only relates to the use safety of the ship, but also is very important to improve the equipment safety and reduce the equipment acquisition cost because the oil cylinder is very expensive in manufacturing cost and the reasonable parameter formulation is key for controlling the cost. At present, no effective theoretical optimization calculation method exists for the stress of the luffing cylinder, the stress is generally calculated through repeated adjustment, and then the maximum pulling force and the maximum pushing force of the luffing cylinder are selected by combining the production capacity and the cost of a cylinder manufacturer.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a stress optimization method for an amplitude variation cylinder of an ultra-large pile driving ship, which can conveniently find the arrangement size of a pile frame and the amplitude variation cylinder when the stress of the amplitude variation cylinder is better without complicated software programming, and provides reliable theoretical guidance for optimizing the stress of the amplitude variation cylinder and the arrangement size of the pile frame.
The purpose of the invention is realized in the following way: a stress optimization method for an amplitude variation oil cylinder of an ultra-large pile driving ship comprises the following steps:
step one, determining design variables, including:
horizontal distance L from lower hinge point of oil cylinder to lower hinge point of pile frame 1 Right + left-;
horizontal distance L from first upper hinge point of oil cylinder to lower hinge point of pile frame 2 Right + left-;
horizontal distance L from second upper hinge point of oil cylinder to lower hinge point of pile frame 3 Right + left-;
vertical distance h from lower hinge point of oil cylinder to lower hinge point of pile frame 1 Upward is +, left is-;
vertical distance h from first upper hinge point of oil cylinder to lower hinge point of pile frame 2 Upward is +, left is-;
vertical distance h from second upper hinge point of oil cylinder to lower hinge point of pile frame 3 Upward is +, left is-;
the included angle a between the pile frame and the vertical direction is clockwise+ and anticlockwise-;
step two, inputting the design variables into Excel software;
step three, determining an objective function, and taking the maximum pulling force and the maximum pushing force of the luffing cylinder as the objective function; the maximum pulling force of the amplitude variation oil cylinder is generated in the working condition of the maximum pile frame, and at the moment, the upper end of a piston rod of the amplitude variation oil cylinder is hinged to a first upper hinging point of the oil cylinder; the maximum thrust of the amplitude variation oil cylinder is generated at the working condition of starting the pile frame, and at the moment, the upper end of a piston rod of the amplitude variation oil cylinder is hinged at a second upper hinge point of the oil cylinder; according to the static equilibrium relation and the geometric relation of the arrangement size of the pile frame and the amplitude variation oil cylinder, the following two calculation formulas of the amplitude variation oil cylinder stress are obtained:
1) When the upper end of a piston rod of the amplitude variation oil cylinder is hinged at a first upper hinge point of the oil cylinder, the maximum pulling force F is calculated by the following formula:
the method is characterized by comprising the following steps: f=f (L 1 ，L 2 ，h 1 ，h 2 ，a)
2) The maximum thrust F is used when the upper end of the piston rod of the amplitude-variable oil cylinder is hinged at the second upper hinge point of the oil cylinder 1 Calculated from the following formula:
the method is characterized by comprising the following steps: f (F) 1 ＝f(L 1 ，L 3 ，h 1 ，h 3 ，a)
Of the two formulas above:
wherein:is a design coefficient; m is M Oil cylinder Moment generated by the amplitude-variable oil cylinder on the lower hinge point of the pile frame; m is M Pile frame Moment generated by the pile frame to the lower hinge point of the pile frame; m is M Pile Moment generated for the pile to the lower hinge point of the pile frame; m is M Hammer Moment generated by the pile hammer on the lower hinge point of the pile frame; m is M Hook Moment generated by the lifting hook on the lower hinge point of the pile frame;
wherein: g is the weight of the pile frame, gx and Gy are coordinates of the gravity center of the pile frame taking the lower hinge point of the pile frame as an origin when the pile frame is in an upright state;
2) The moment generated by the pile to the lower hinge point of the pile frame is calculated by the following formula:
wherein: g 1 Gx is the weight of the pile 1 ，Gy 1 When the pile frame is in an upright state, the gravity center of the pile takes the lower hinge point of the pile frame as the origin coordinate;
3) The moment generated by the pile hammer on the lower hinge point of the pile frame is calculated by the following formula:
wherein: g 2 Gx is the weight of the pile hammer 2 ，Gy 2 When the pile frame is in an upright state, the gravity center of the pile hammer takes a lower hinge point of the pile frame as an origin coordinate;
4) The moment generated by the lifting hook on the lower hinge point of the pile frame is calculated by the following formula:
wherein: g 3 Gx is the weight of the hook 3 ，Gy 3 When the pile frame is in an upright state, the gravity center of the lifting hook takes the lower hinge point of the pile frame as the origin coordinate;
step four, determining constraint conditions, including:
(1) The included angle between the pile frame and the vertical direction is a when the pile frame is in a resting state 0 When the pile frame rear included angle structure is restrained from interfering with the main deck, namely the distance from the bottom of the pile frame rear included angle structure to the main deck is R 1 ：
Wherein: Δh is the set safety height from the bottom of the pile frame rear included angle structure to the main deck; r is the arc radius of the pile frame rear included angle structure; h is the distance from the lower hinge point of the oil cylinder to the main deck;
(2) The maximum installation length L' max of the upper end of the piston rod of the amplitude-variable oil cylinder when hinged at the second upper hinging point of the oil cylinder is restrained to be approximately equal to the maximum installation length Lmax of the upper end of the piston rod of the amplitude-variable oil cylinder when hinged at the first upper hinging point of the oil cylinder within 200 mm;
the mounting length of the piston rod upper end of the amplitude variation oil cylinder when hinged at the second upper hinge point of the oil cylinder is as follows:
the installation length of the upper end of the piston rod of the amplitude variation oil cylinder when hinged at the first upper hinge point of the oil cylinder is as follows:
namely: l (L) max ≈L’ max
(3) The method comprises the steps that the minimum installation length L' min when the upper end of a piston rod of the amplitude-variable oil cylinder is hinged to a second upper hinging point of the oil cylinder is restrained to be approximately equal to the minimum installation length Lmin when the upper end of the piston rod of the amplitude-variable oil cylinder is hinged to a first upper hinging point of the oil cylinder within 200 mm;
namely L min ≈L’ min
(4) Restraining the self structure of the luffing cylinder, namely, the difference between the minimum installation length of the luffing cylinder and the stroke of the luffing cylinder is not smaller than a set value C; the maximum installation length of the luffing cylinder and the minimum installation length of the luffing cylinder are both considered to be the design allowance delta S, and the stroke S of the luffing cylinder is calculated by the following formula:
S＝(Max{L max ，L' max }+Δs)-(Min{L min ，L’ min }-Δs)
＝Max{L max ，L' max }-Min{L min ，L’ min }+2Δs
the stroke difference between the minimum installation length of the amplitude variation oil cylinder and the amplitude variation oil cylinder is not smaller than a set value C:
(Min{L min ，L’ min }-Δs)-S≥C
namely: 2Min { L min ，L’ min }-Max{L max ，L' max }-3Δs≥C
Fifthly, inputting the objective function and the constraint condition into Excel software to perform stress optimization calculation of the luffing cylinder.
The stress optimization method for the amplitude variation oil cylinder of the ultra-large pile driving ship comprises the following steps of:
1) A single design variable research method is adopted, namely, one design variable is taken as a research object, and the relation between the stress of the variable amplitude oil cylinder and the design variable is researched under the condition that the other design variables are given values; discretizing the design variable on the values, calculating the stress of the variable amplitude oil cylinder corresponding to each value, and finishing the stress into a table or a chart, wherein the influence of the stress of the variable amplitude oil cylinder relative to different values of the design variable is seen from the table or the chart;
2) According to the magnitude of the stress influence on the variable amplitude oil cylinder when each design variable value changes per unit, the design variables are sequenced in a primary and secondary mode, and the horizontal distance L from the lower hinge point of the oil cylinder to the lower hinge point of the pile frame of the maximum thrust of the variable amplitude oil cylinder is obtained 1 The influence of the oil cylinder is the largest, and the vertical distance h from the lower hinge point of the oil cylinder to the lower hinge point of the pile frame is the second 1 The method comprises the steps of carrying out a first treatment on the surface of the The maximum pulling force of the amplitude variation oil cylinder is subject to the horizontal distance L from the lower hinging point of the oil cylinder to the lower hinging point of the pile frame 1 The influence is the greatest, and secondly, the horizontal distance L from the first upper hinge point of the oil cylinder to the lower hinge point of the pile frame 2 The stress of other variables on the amplitude-variable oil cylinder is slightly influenced;
3) During optimization calculation, the design variables are valued one by one according to the sequence from the main design variable to the secondary design variable, namely, the numerical value of the main design variable is determined firstly, and then the numerical value of the secondary design variable is determined according to constraint conditions, so that the optimized amplitude variation oil cylinder stress can be obtained.
The stress optimization method of the amplitude-variable oil cylinder of the ultra-large pile driving ship has the following characteristics: the arrangement size of the pile frame and the amplitude variation oil cylinder when the stress of the amplitude variation oil cylinder is better can be conveniently found by simply editing all parameters and formulas into Excel software and simply calculating the Excel software without complicated software programming, so that reliable theoretical guidance is provided for optimizing the stress of the amplitude variation oil cylinder and the arrangement size of the pile frame, the compactness and the stability of the arrangement structure of the pile frame and the amplitude variation oil cylinder are improved, and the service life of the amplitude variation oil cylinder is prolonged.
Drawings
Fig. 1 is a schematic structural view of the positional relationship between a pile frame and an amplitude cylinder of an oversized pile driving vessel of the present invention (in four states);
FIG. 2 is a simplified diagram of the positional relationship between the pile frame and the luffing cylinder (before the luffing cylinder is hinged) of the oversized piling ship;
fig. 3 is a simplified diagram of the positional relationship between the pile frame and the luffing cylinder of the oversized pile driving vessel (after the luffing cylinder is hinged).
Detailed Description
The invention will be further described with reference to the accompanying drawings.
Referring to fig. 1 to 3, the stress optimization method of the amplitude variation cylinder of the ultra-large pile driving ship of the invention comprises the following steps:
step one, determining design variables, including the structures of all pile frames 200 influencing the stress of the luffing cylinder 100 and the arrangement positions of the lower hinging point of the cylinder and the upper hinging points of the two cylinders; the design variables include:
horizontal distance L from lower hinge point 10 of oil cylinder to lower hinge point 20 of pile frame 1 Right + left-;
horizontal distance L from first upper hinge point 11 of oil cylinder to lower hinge point 20 of pile frame 2 Right + left-;
horizontal distance L from second upper hinge point 12 of oil cylinder to lower hinge point 20 of pile frame 3 Right +, left +-；
Vertical distance h from cylinder lower hinge point 10 to pile frame lower hinge point 20 1 Upward is +, left is-;
vertical distance h from first upper hinge point 11 of oil cylinder to lower hinge point 20 of pile frame 2 Upward is +, left is-;
vertical distance h from second upper hinge point 12 of oil cylinder to lower hinge point 20 of pile frame 3 Upward is +, left is-;
the included angle a between the pile frame 200 and the vertical direction is clockwise +, anticlockwise-;
step two, inputting all the design variables into Excel software;
step three, determining an objective function, and taking the maximum pulling force and the maximum pushing force of the luffing cylinder as the objective function; the maximum pulling force of the luffing cylinder 100 occurs in the working condition of the maximum pile frame, the pile load exists at the moment, the pile hammer is positioned at the top of the pile frame 200, and at the moment, the upper end of a piston rod of the luffing cylinder 100 is hinged at a cylinder first upper hinge point 11 (see figure 2); the maximum thrust of the luffing cylinder 100 occurs at the beginning of the pile frame working condition, and at the moment, the upper end of a piston rod of the luffing cylinder 100 is hinged at a cylinder second upper hinge point 12 (see figure 3); the following two calculation formulas of the amplitude cylinder stress are obtained according to the static equilibrium relation and the geometric relation of the arrangement sizes of the pile frame 200 and the amplitude cylinder 100:
1) When the upper end of the piston rod of the luffing cylinder 100 is hinged at the first upper hinge point 11 of the cylinder, the maximum pulling force F used is calculated by the following formula:
the method is characterized by comprising the following steps: f=f (L 1 ，L 2 ，h 1 ，h 2 ，a)
2) Maximum thrust F used when the upper end of the piston rod of the luffing cylinder 100 is hinged at the second upper hinging point 12 of the cylinder 1 Calculated from the following formula:
the method is characterized by comprising the following steps: f (F) 1 ＝f(L 1 ，L 3 ，h 1 ，h 3 ，a)
Of the two formulas above:
wherein:is a design coefficient; m is M Oil cylinder Moment generated by the amplitude variation oil cylinder 100 on the pile frame lower hinge point 20; m is M Pile frame Moment generated for the pile frame 200 to the pile frame lower hinge point 20; m is M Pile Moment generated for pile-to-pile frame lower hinge point 20; m is M Hammer Moment generated for the pile hammer to the pile frame lower hinge point 20; m is M Hook Moment generated for the hook to the pile frame lower hinge point 20;
the pile driving ship adopts the amplitude-variable oil cylinder 100 to drive the pile frame 200 to carry out amplitude variation, and when the pile frame works, the moment generated by the pile frame, the pile hammer and the lifting hook on the pile frame lower hinge point 20 due to dead weight is balanced by the moment of the amplitude-variable oil cylinder 100 on the pile frame lower hinge point 20;
wherein: g is the weight of the pile frame, gx and Gy are coordinates of the gravity center of the pile frame taking the lower hinge point of the pile frame as an origin when the pile frame is in an upright state;
2) The moment generated by the pile to the lower hinge point of the pile frame is calculated by the following formula:
wherein: g 1 Gx is the weight of the pile 1 ，Gy 1 When the pile frame is in an upright state, the gravity center of the pile takes the lower hinge point of the pile frame as the origin coordinate;
3) The moment generated by the pile hammer on the lower hinge point of the pile frame is calculated by the following formula:
wherein: g 2 Gx is the weight of the pile hammer 2 ，Gy 2 When the pile frame is in an upright state, the gravity center of the pile hammer takes a lower hinge point of the pile frame as an origin coordinate;
4) The moment generated by the lifting hook on the lower hinge point of the pile frame is calculated by the following formula:
wherein: g 3 Gx is the weight of the hook 3 ，Gy 3 When the pile frame is in an upright state, the gravity center of the lifting hook takes the lower hinge point of the pile frame as the origin coordinate;
determining constraint conditions, including the following four constraint conditions:
(1) In the resting state of the pile frame 200, the included angle between the pile frame 200 and the vertical direction is a 0 When the pile frame rear included angle structure 201 is not interfered with the main deck 30, i.e. the distance from the bottom of the pile frame rear included angle structure 201 to the main deck 30 is R 1 ：
Wherein: Δh is the set safety height from the bottom of the pile frame rear included angle structure to the main deck; r is the arc radius of the pile frame rear included angle structure 201; h is the distance from the oil cylinder lower hinge point 10 to the main deck 30;
(2) The maximum installation length L' max of the upper end of the piston rod of the amplitude-variable oil cylinder when hinged at the second upper hinging point of the oil cylinder is restrained to be approximately equal to the maximum installation length Lmax of the upper end of the piston rod of the amplitude-variable oil cylinder when hinged at the first upper hinging point of the oil cylinder within 200 mm;
the mounting length of the piston rod upper end of the amplitude variation oil cylinder when hinged at the second upper hinge point of the oil cylinder is as follows:
the installation length of the upper end of the piston rod of the amplitude variation oil cylinder when hinged at the first upper hinge point of the oil cylinder is as follows:
namely: l (L) max ≈L’ max
(3) The method comprises the steps that the minimum installation length L' min when the upper end of a piston rod of the amplitude-variable oil cylinder is hinged to a second upper hinging point of the oil cylinder is restrained to be approximately equal to the minimum installation length Lmin when the upper end of the piston rod of the amplitude-variable oil cylinder is hinged to a first upper hinging point of the oil cylinder within 200 mm;
namely L min ≈L’ min
(4) Restraining the self structure of the luffing cylinder, namely, the difference between the minimum installation length of the luffing cylinder and the stroke of the luffing cylinder is not smaller than a set value C; the maximum installation length of the luffing cylinder and the minimum installation length of the luffing cylinder are both considered to be the design allowance delta S, and the stroke S of the luffing cylinder is calculated by the following formula:
S＝(Max{L max ，L' max }+Δs)-(Min{L min ，L’ min }-Δs)
＝Max{L max ，L' max }-Min{L min ，L’ min }+2Δs
the stroke difference between the minimum installation length of the amplitude variation oil cylinder and the amplitude variation oil cylinder is not smaller than a set value C:
(Min{L min ，L’ min }-Δs)-S≥C
namely: 2Min { L min ，L’ min }-Max{L max ，L' max }-3Δs≥C
Inputting the objective function and the constraint condition into Excel software, and performing stress optimization calculation of the luffing cylinder, wherein the stress optimization calculation is performed specifically according to the following method:
1) A single design variable research method is adopted, namely, one design variable is taken as a research object, and the relation between the stress of the variable amplitude oil cylinder and the design variable is researched under the condition that the other design variables are given values; discretizing the design variable on the values, calculating the stress of the variable amplitude oil cylinder corresponding to each value, and finishing the stress into a table or a chart, wherein the influence of the stress of the variable amplitude oil cylinder relative to different values of the design variable is seen from the table or the chart;
2) According to the stress influence of each design variable value on the variable amplitude oil cylinder in unit change, the design variables are sequenced in a primary and secondary mode to obtain the horizontal distance L from the lower hinge point of the oil cylinder to the lower hinge point of the pile frame of the maximum thrust of the variable amplitude oil cylinder 1 The influence of the oil cylinder is the largest, and the vertical distance h from the lower hinge point of the oil cylinder to the lower hinge point of the pile frame is the second 1 The method comprises the steps of carrying out a first treatment on the surface of the The maximum pulling force of the amplitude variation oil cylinder is subject to the horizontal distance L from the lower hinging point of the oil cylinder to the lower hinging point of the pile frame 1 The influence is the greatest, and secondly, the horizontal distance L from the first upper hinge point of the oil cylinder to the lower hinge point of the pile frame 2 The stress of other variables on the amplitude-variable oil cylinder is slightly influenced;
3) During optimization calculation, the design variables are valued one by one according to the sequence from the main design variable to the secondary design variable, namely, the numerical value of the main design variable is determined firstly, and then the numerical value of the secondary design variable is determined according to constraint conditions, so that the optimized amplitude variation oil cylinder stress can be obtained.
The invention will now be described by taking a 133-meter oversized pile driving vessel as an example:
1. inputting parameters
1. Inputting design variables
Horizontal distance L from lower hinge point 10 of oil cylinder to lower hinge point 20 of pile frame 1 Vertical distance h from oil cylinder lower hinge point 10 to pile frame lower hinge point 20 of = -17700mm 1 Horizontal distance L from cylinder first upper hinge point 11 to pile frame lower hinge point 20 = -8700mm 2 Vertical distance h from first upper hinge point 11 of oil cylinder to lower hinge point 20 of pile frame 2 Horizontal distance L from cylinder second upper hinge point 12 to pile frame lower hinge point 20 =19000 mm 3 Vertical distance h from second upper hinge point 12 of oil cylinder to lower hinge point 20 of pile frame = -1820mm 3 ＝28910mm。
2. Inputting parameters for calculating moment
Weight G of pile frame and pile frameBarycentric coordinates Gx, gy, weight G of pile 1 Barycentric coordinates Gx of pile 1 、Gy 1 Weight G of hammer 2 Barycentric coordinates Gx of the hammer 2 、Gy 2 Weight G of hook 3 Barycentric coordinates Gx of the hook 3 、Gy 3 The values of (2) are as follows:
G＝840t，Gx＝-2300mm，Gy＝47000mm；
G 1 ＝300t，Gx 1 ＝3530mm，Gy 1 take G during non-pile driving conditions = 37100mm 1 ＝0；
G 2 ＝280t，Gx 2 ＝3530mm，Gy 2 The barycentric coordinates of the hammer are considered as being positioned at the hinge-exchanging cross beam when the pile frame is in a laying working condition, namely, gy is taken 2 ＝h 2 ；
G 3 ＝60t，Gx 3 ＝3530mm，Gy 3 91950mm, the hook is positioned at the hook sealing position on the hinge-replaced cross beam when the pile frame is in a placing working condition, gx3=0 and gyr3=h2 are taken;
the value of the included angle a between the pile frame and the vertical direction:
maximum tension condition: a=14°; the maximum thrust working condition is as follows: a= -70.5 °; when the amplitude-variable oil cylinder is hinged: a= -27 °; when the pile frame is inclined forwards maximally: a=22°.
3. Inputting design coefficient for calculating stress of amplitude-variable oil cylinderMaximum tension condition: />When the working condition of maximum thrust is:>
2. calculating the maximum pulling force F of the luffing cylinder under the working condition of the maximum pile frame, wherein the upper end of a piston rod of the luffing cylinder 100 is hinged at a first upper hinging point 11 of the cylinder, and an included angle a=14 DEG between the pile frame 200 and the vertical direction;
calculating pile frame-to-pile frame lower hinge point production in Excel softwareMoment M of generation Pile frame ：
Calculating moment M generated by piles on lower hinge points of pile frames in Excel software according to the following formula Pile ：
In Excel software, calculating moment M generated by the hammer on the lower hinge point of the pile frame according to the following formula Hammer ：
In Excel software, calculating moment M generated by the lifting hook on the lower hinge point of the pile frame according to the following formula Hook ：
Calculating moment M generated by the luffing cylinder on a lower hinge point of the pile frame in Excel software according to the following formula Oil cylinder ：
The installation length L of the luffing cylinder is calculated in Excel software according to the following formula:
the maximum pulling force F of the luffing cylinder was calculated in Excel software according to the following formula:
3. calculating the maximum thrust F of the variable amplitude oil cylinder under the working condition of starting the pile frame 1 At this time, the upper end of the piston rod of the amplitude cylinder 100 is hinged to the second upper hinging point 12 of the cylinder, and the included angle a between the pile frame 200 and the vertical direction is between 70.5 and a=;
calculating moment M generated by pile frame on pile frame lower hinge point in Excel software according to the following formula Pile frame ：
Calculating moment M generated by piles on lower hinge points of pile frames in Excel software according to the following formula Pile ：
In Excel software, calculating moment M generated by the hammer on the lower hinge point of the pile frame according to the following formula Hammer ：
In Excel software, calculating moment M generated by the lifting hook on the lower hinge point of the pile frame according to the following formula Hook ：
Calculating moment M generated by the luffing cylinder on a lower hinge point of the pile frame in Excel software according to the following formula Oil cylinder ：
The installation length L' of the luffing cylinder is calculated in Excel software according to the following formula:
calculating the maximum thrust F of the luffing cylinder in Excel software according to the following formula 1 ：
4. Editing calculation formulas of four constraint conditions in Excel software, wherein the calculation formulas are used for judging whether the values of design variables meet the constraint conditions or not;
constraint (1): when the pile frame is placed, the included angle a between the pile frame and the vertical direction 0 The arc radius R=1750 mm of the back included angle structure is between 70.5 degrees and 70 degrees, the distance from the lower hinge point of the oil cylinder to the main deck is h=1100 mm, the set safety height delta h=300 mm from the bottom of the pile frame rear angle structure to the main deck, namely the height R from the bottom of the pile frame rear angle structure to the main deck 1 Calculated from the following formula:
constraint (2): maximum installation length of variable-amplitude oil cylinder
When the upper end of a piston rod of the luffing cylinder is hinged to a second upper hinge point of the cylinder, the included angle a= -27 degrees between a pile frame and the vertical direction when the luffing cylinder is hinged is corresponding, and the maximum installation length of the luffing cylinder is calculated by the following formula:
when the upper end of a piston rod of the amplitude variation oil cylinder is hinged to a first upper hinging point of the oil cylinder, the included angle a=22° between the pile frame and the vertical direction when the corresponding pile frame is inclined forwards maximally, and the maximum mounting length of the amplitude variation oil cylinder is calculated by the following formula:
lmax= 33737.31 (mm), L' max= 33762.17 (mm), difference=24.86, and within 200mm of each other, i.e. constrained to be approximately equal, i.e. L max (a＝22)≈L’ max (a＝-27)
Constraint (3): minimum mounting length of luffing cylinder
When the upper end of a piston rod of the luffing cylinder is hinged to a second upper hinging point of the cylinder, an included angle a= -70.5 degrees between the pile frame and the vertical direction when the corresponding pile frame is placed, and the minimum mounting length of the luffing cylinder is calculated by the following formula:
when the upper end of a piston rod of the luffing cylinder is hinged to a first upper hinging point of the cylinder, an included angle a= -27 degrees between a pile frame and the vertical direction when the luffing cylinder is hinged is corresponding, and the minimum mounting length of the luffing cylinder is calculated by the following formula:
lmin= 19352.13 (mm), L' min= 19491.69 (mm), difference= 139.56, and constraints within 200mm are approximately equal; namely:
L min (a＝-27)≈L’ min (a＝-70.5)
constraint (4): the difference between the minimum installation length of the luffing cylinder and the travel of the luffing cylinder is not smaller than a set value C, the value C is selected and determined according to the design requirements of different cylinder manufacturers, the C=4200mm is adopted in the embodiment, and the design allowance deltas=200mm of the maximum installation length and the minimum installation length of the luffing cylinder is obtained, namely
2Min{L min ，L’ min }-Max{L max ，L' max )}＝4942.092342≥4800
5. The method adopts a single design variable research method, namely, one design variable is firstly used as a research object, and the relation between the stress of the variable amplitude oil cylinder and the design variable is researched under the condition that the other design variables are given values. The design variable is subjected to discretization processing on the values, the stress of the amplitude variation oil cylinder corresponding to each value is calculated, and the stress of the amplitude variation oil cylinder is arranged into a table or a chart, so that the influence of different values of the stress of the amplitude variation oil cylinder relative to the design variable can be intuitively seen. In order to facilitate data analysis, other design variables are processed according to the finally adopted numerical value of the piling ship, so that the judgment of the variation trend of the stress of each design variable on the amplitude-variable oil cylinder is not influenced; namely:
when the horizontal distance L from the lower hinge point of the oil cylinder to the lower hinge point of the pile frame is researched 1 H is in stress change relation with the amplitude-variable oil cylinder 1 ，L 2 ，h 2 ，L 3 And h 3 Setting according to the data; the second upper hinge point of the oil cylinder is more beneficial to structural design on the premise of meeting the size of the end head of the piston rod of the amplitude-variable oil cylinder, and the closer to the front chord of the pile frame, the more beneficial to structural design, thus L 3 The change of the value of the variable amplitude oil cylinder on the stress of the variable amplitude oil cylinder is small, and the analysis can be omitted.
The calculation results are arranged in tables 1 to 5; ok in the table indicates that the constraint is correct and error indicates that the constraint is incorrect.
Table 1 shows the maximum stress and maximum tension of the luffing cylinder and L 1 Relation of (2)
Table 2 shows the maximum stress and maximum tension of the luffing cylinder and h 1 Relation of (2)
| h 1 ，mm | Maximum tension, t | Maximum thrust, t | Constraint 1 | Constraint 2 | Constraint 3 | Constraint 4 |
| -8300 | 1692.4 | -2697.1 | error | ok | ok | error |
| -8400 | 1694.1 | -2688.9 | error | ok | ok | error |
| -8500 | 1695.8 | -2680.9 | error | ok | ok | error |
| -8600 | 1697.5 | -2672.9 | ok | ok | ok | ok |
| -8700 | 1699.2 | -2665.1 | ok | ok | ok | ok |
| -8800 | 1700.9 | -2657.5 | ok | ok | ok | ok |
| -8900 | 1702.6 | -2649.9 | ok | ok | ok | ok |
| -9000 | 1704.3 | -2642.5 | ok | ok | ok | ok |
Table 3 shows the maximum pushing force and the maximum pulling force of the luffing cylinder and L 2 Relation of (2)
| L 2 ，mm | Maximum tension, t | Maximum thrust, t | Constraint 1 | Constraint 2 | Constraint 3 | Constraint 4 |
| -13600 | 1757.5 | -2665.1 | ok | ok | ok | ok |
| -13900 | 1742.4 | -2665.1 | ok | ok | ok | ok |
| -14200 | 1727.6 | -2665.1 | ok | ok | ok | ok |
| -14500 | 1713.2 | -2665.1 | ok | ok | ok | ok |
| -14800 | 1699.2 | -2665.1 | ok | ok | ok | ok |
| -15100 | 1685.6 | -2665.1 | error | ok | error | error |
| -15400 | 1672.4 | -2665.1 | error | ok | error | error |
| -15700 | 1659.5 | -2665.1 | error | ok | error | error |
Table 4 shows the maximum pushing force and the maximum pulling force of the luffing cylinder and h 2 Relation of (2)
| h 2 ，mm | Maximum tension, t | Maximum thrust, t | Constraint 1 | Constraint 2 | Constraint 3 | Constraint 4 |
| 18100 | 1699.6 | -2647.5 | error | error | error | error |
| 18400 | 1699.5 | -2653.4 | error | error | error | error |
| 18700 | 1699.4 | -2659.3 | ok | error | error | error |
| 19000 | 1699.2 | -2665.1 | ok | ok | ok | ok |
| 19300 | 1699.1 | -2671.0 | ok | error | ok | ok |
| 19600 | 1699.0 | -2676.9 | ok | error | error | error |
| 19900 | 1698.9 | -2682.8 | ok | error | error | error |
| 20200 | 1698.8 | -2688.6 | ok | error | error | error |
| 20500 | 1698.7 | -2694.5 | ok | error | error | error |
| 20800 | 1698.6 | -2700.4 | ok | error | error | error |
| 21100 | 1698.5 | -2706.3 | ok | error | error | error |
Table 5 shows the maximum pushing force and the maximum pulling force of the luffing cylinder and h 3 Relation of (2)
6. Stress optimization analysis and conclusion of amplitude-variable oil cylinder
As can be seen from tables 1 to 5:
a) Horizontal distance L from lower hinge point of oil cylinder to lower hinge point of pile frame 1 The influence on the maximum pushing force and the maximum pulling force of the luffing cylinder is most remarkable, and the maximum pushing force and the maximum pulling force of the luffing cylinder are along with L 1 Is decreased by an increase in (c). The selection point of the luffing cylinder should be preferentially determined to be L 1 The method comprises the steps of carrying out a first treatment on the surface of the On the premise of meeting other constraint conditions, L 1 The value should be as large as possible.
B) Horizontal distance L from first upper hinge point of oil cylinder to lower hinge point of pile frame 2 The maximum thrust of the amplitude variation oil cylinder is irrelevant, and the maximum pulling force of the amplitude variation oil cylinder is relevant only to the maximum pulling force of the amplitude variation oil cylinder, and the maximum pulling force of the amplitude variation oil cylinder is along with L 2 Increase and decrease; at the same time, the L 2 Enlargement can also be achievedIncreasing the overall maximum bending-resistant section modulus of the pile frame structure, so that under the condition of meeting constraint conditions, L 2 The value should be as large as possible.
C) Vertical distance h from lower hinge point of oil cylinder to lower hinge point of pile frame 1 The maximum tensile force of the luffing cylinder is slightly influenced, the maximum thrust of the luffing cylinder is influenced to a certain extent, h 1 The larger the value is, the smaller the maximum thrust of the amplitude variation oil cylinder is, but the larger the height of the pile frame is after being laid down, the ship navigation height can be influenced; the actual selection can be determined according to the specific navigation height requirement, and if the navigation height requirement is not strict, h can be properly reduced 1 Is a value of (a).
D) Vertical distance h from first upper hinge point of oil cylinder to lower hinge point of pile frame 2 And the vertical distance h from the second upper hinge point of the oil cylinder to the lower hinge point of the pile frame 3 The value of the variable amplitude oil cylinder has small stress influence on the variable amplitude oil cylinder, and mainly influences the maximum installation distance and the minimum installation distance of the variable amplitude oil cylinder, and the installation distance of the variable amplitude oil cylinder is along with h 2 And h 3 The increase is obviously increased, but the theoretical stroke change of the amplitude variation oil cylinder is not great; the increased mounting distance of the luffing cylinder means that the effective stroke of the luffing cylinder is not fully utilized, which would result in unnecessary cost increase.
E) According to analysis, selecting a horizontal distance L from a lower hinge point of the oil cylinder to a lower hinge point of the pile frame 1 Vertical distance h from oil cylinder lower hinge point to pile frame lower hinge point of = -17700mm 1 Horizontal distance L from first upper hinge point of oil cylinder to lower hinge point of pile frame = -8700mm 2 Vertical distance h from first upper hinge point of oil cylinder to lower hinge point of pile frame 2 Horizontal distance L from second upper hinge point of cylinder to lower hinge point of pile frame =19000 mm 3 Vertical distance h from second upper hinge point of oil cylinder to lower hinge point of pile frame 3 The value of the variable amplitude oil cylinder is 28910mm, so that the aim of optimizing the stress of the variable amplitude oil cylinder is basically fulfilled.
According to the stress optimization method for the amplitude cylinder of the ultra-large pile driving ship, complicated software programming is not needed, all calculation formulas of design variables and constraint conditions and calculation formulas of objective functions are only edited into Excel software, and the arrangement size of the pile frame and the amplitude cylinder when the stress of the amplitude cylinder is better can be conveniently found through simple calculation of the Excel software, so that reliable theoretical guidance is provided for optimizing the stress of the amplitude cylinder and the arrangement size of the pile frame, the compactness and the stability of the arrangement structure of the pile frame and the amplitude cylinder are improved, and the service life of the amplitude cylinder is prolonged.
The above embodiments are provided for illustrating the present invention and not for limiting the present invention, and various changes and modifications may be made by one skilled in the art without departing from the spirit and scope of the present invention, and thus all equivalent technical solutions should be defined by the claims.
Claims (2)
1. The stress optimization method of the amplitude variation oil cylinder of the ultra-large pile driving ship is characterized by comprising the following steps of:
step one, determining design variables, including:
horizontal distance L from lower hinge point of oil cylinder to lower hinge point of pile frame 1 Right + left-;
horizontal distance L from first upper hinge point of oil cylinder to lower hinge point of pile frame 2 Right + left-;
horizontal distance L from second upper hinge point of oil cylinder to lower hinge point of pile frame 3 Right + left-;
vertical distance h from lower hinge point of oil cylinder to lower hinge point of pile frame 1 Upward is +, left is-;
vertical distance h from first upper hinge point of oil cylinder to lower hinge point of pile frame 2 Upward is +, left is-;
vertical distance h from second upper hinge point of oil cylinder to lower hinge point of pile frame 3 Upward is +, left is-;
the included angle a between the pile frame and the vertical direction is clockwise+ and anticlockwise-;
step two, inputting the design variables into Excel software;
step three, determining an objective function, and taking the maximum pulling force and the maximum pushing force of the luffing cylinder as the objective function; the maximum pulling force of the amplitude variation oil cylinder is generated in the working condition of the maximum pile frame, and at the moment, the upper end of a piston rod of the amplitude variation oil cylinder is hinged to a first upper hinging point of the oil cylinder; the maximum thrust of the amplitude variation oil cylinder is generated at the working condition of starting the pile frame, and at the moment, the upper end of a piston rod of the amplitude variation oil cylinder is hinged at a second upper hinge point of the oil cylinder; according to the static equilibrium relation and the geometric relation of the arrangement size of the pile frame and the amplitude variation oil cylinder, the following two calculation formulas of the amplitude variation oil cylinder stress are obtained:
1) When the upper end of a piston rod of the amplitude variation oil cylinder is hinged at a first upper hinge point of the oil cylinder, the maximum pulling force F is calculated by the following formula:
the method is characterized by comprising the following steps: f=f (L 1 ，L 2 ，h 1 ，h 2 ，a)
2) The maximum thrust F is used when the upper end of the piston rod of the amplitude-variable oil cylinder is hinged at the second upper hinge point of the oil cylinder 1 Calculated from the following formula:
the method is characterized by comprising the following steps: f (F) 1 ＝f(L 1 ，L 3 ，h 1 ，h 3 ，a)
Of the two formulas above:
wherein:is a design coefficient; m is M Oil cylinder Moment generated by the amplitude-variable oil cylinder on the lower hinge point of the pile frame; m is M Pile frame Moment generated by the pile frame to the lower hinge point of the pile frame; m is M Pile Moment generated for the pile to the lower hinge point of the pile frame; m is M Hammer Moment generated by the pile hammer on the lower hinge point of the pile frame; m is M Hook Moment generated by the lifting hook on the lower hinge point of the pile frame;
wherein: g is the weight of the pile frame, gx and Gy are coordinates of the gravity center of the pile frame taking the lower hinge point of the pile frame as an origin when the pile frame is in an upright state;
2) The moment generated by the pile to the lower hinge point of the pile frame is calculated by the following formula:
wherein: g 1 Gx is the weight of the pile 1 ，Gy 1 When the pile frame is in an upright state, the gravity center of the pile takes the lower hinge point of the pile frame as the origin coordinate;
3) The moment generated by the pile hammer on the lower hinge point of the pile frame is calculated by the following formula:
wherein: g 2 Gx is the weight of the pile hammer 2 ，Gy 2 When the pile frame is in an upright state, the gravity center of the pile hammer takes a lower hinge point of the pile frame as an origin coordinate;
4) The moment generated by the lifting hook on the lower hinge point of the pile frame is calculated by the following formula:
wherein: g 3 Gx is the weight of the hook 3 ，Gy 3 When the pile frame is in an upright state, the gravity center of the lifting hook takes the lower hinge point of the pile frame as the origin coordinate;
step four, determining constraint conditions, including:
(1) The included angle between the pile frame and the vertical direction is a when the pile frame is in a resting state 0 When the pile frame rear included angle structure is restrained from interfering with the main deck, namely the distance from the bottom of the pile frame rear included angle structure to the main deck is R 1 ：
Wherein: Δh is the set safety height from the bottom of the pile frame rear included angle structure to the main deck; r is the arc radius of the pile frame rear included angle structure; h is the distance from the lower hinge point of the oil cylinder to the main deck;
(2) Maximum installation length L 'when the upper end of a piston rod of the amplitude variable oil cylinder is hinged to a second upper hinge point of the oil cylinder' max Maximum mounting length L when hinged with upper end of piston rod of amplitude-variable oil cylinder at first upper hinge point of oil cylinder max The constraint is approximately equal within 200 mm;
the mounting length of the piston rod upper end of the amplitude variation oil cylinder when hinged at the second upper hinge point of the oil cylinder is as follows:
the installation length of the upper end of the piston rod of the amplitude variation oil cylinder when hinged at the first upper hinge point of the oil cylinder is as follows:
namely: l (L) max ≈L’ max
(3) Minimum mounting length L 'when the upper end of a piston rod of the amplitude variable oil cylinder is hinged to a second upper hinge point of the oil cylinder' min Minimum mounting length L when being hinged with upper end of piston rod of amplitude-variable oil cylinder at first upper hinge point of oil cylinder min The constraint is approximately equal within 200 mm;
namely L min ≈L’ min
(4) Restraining the self structure of the luffing cylinder, namely, the difference between the minimum installation length of the luffing cylinder and the stroke of the luffing cylinder is not smaller than a set value C; the maximum installation length of the luffing cylinder and the minimum installation length of the luffing cylinder are both considered to be the design allowance delta S, and the stroke S of the luffing cylinder is calculated by the following formula:
S＝(Max{L max ，L' max }+Δs)-(Min{L min ，L’ min }-Δs)
＝Max{L max ，L' max }-Min{L min ，L’ min }+2Δs
the stroke difference between the minimum installation length of the amplitude variation oil cylinder and the amplitude variation oil cylinder is not smaller than a set value C:
(Min{L min ，L’ min }-Δs)-S≥C
namely: 2Min { L min ，L’ min }-Max{L max ，L' max }-3Δs≥C
Fifthly, inputting the objective function and the constraint condition into Excel software to perform stress optimization calculation of the luffing cylinder.
2. The stress optimization method for the luffing cylinder of the oversized pile driving vessel according to claim 1, wherein in the fifth step, the stress optimization calculation for the luffing cylinder is specifically performed by adopting the following method:
1) A single design variable research method is adopted, namely, one design variable is taken as a research object, and the relation between the stress of the variable amplitude oil cylinder and the design variable is researched under the condition that the other design variables are given values; discretizing the design variable on the values, calculating the stress of the variable amplitude oil cylinder corresponding to each value, and finishing the stress into a table or a chart, wherein the influence of the stress of the variable amplitude oil cylinder relative to different values of the design variable is seen from the table or the chart;
2) According to the magnitude of the stress influence on the variable amplitude oil cylinder when each design variable value changes per unit, the design variables are sequenced in a primary and secondary mode, and the horizontal distance L from the lower hinge point of the oil cylinder to the lower hinge point of the pile frame of the maximum thrust of the variable amplitude oil cylinder is obtained 1 The influence of the oil cylinder is the largest, and the vertical distance h from the lower hinge point of the oil cylinder to the lower hinge point of the pile frame is the second 1 The method comprises the steps of carrying out a first treatment on the surface of the The maximum pulling force of the amplitude variation oil cylinder is subject to the horizontal distance L from the lower hinging point of the oil cylinder to the lower hinging point of the pile frame 1 The influence is the greatest, and secondly, the horizontal distance L from the first upper hinge point of the oil cylinder to the lower hinge point of the pile frame 2 The stress of other variables on the amplitude-variable oil cylinder is slightly influenced;
3) During optimization calculation, the design variables are valued one by one according to the sequence from the main design variable to the secondary design variable, namely, the numerical value of the main design variable is determined firstly, and then the numerical value of the secondary design variable is determined according to constraint conditions, so that the optimized amplitude variation oil cylinder stress can be obtained.
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