CN112989571A - Stress optimization method for variable-amplitude oil cylinder of ultra-large pile driving barge - Google Patents

Stress optimization method for variable-amplitude oil cylinder of ultra-large pile driving barge Download PDF

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CN112989571A
CN112989571A CN202110174330.2A CN202110174330A CN112989571A CN 112989571 A CN112989571 A CN 112989571A CN 202110174330 A CN202110174330 A CN 202110174330A CN 112989571 A CN112989571 A CN 112989571A
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oil cylinder
hinge point
pile frame
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amplitude
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CN112989571B (en
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孙钦阳
沈火群
胡灵斌
陈雪峰
胡敏
郭亭
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CCCC Third Harbor Engineering Co Ltd
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Abstract

The invention discloses a stress optimization method for a luffing cylinder of an ultra-large pile driving barge, which comprises the following steps of: determining a design variable; inputting design variables into Exce l software; determining an objective function: the maximum pulling force and the maximum pushing force of the oil cylinder; determining a constraint condition: in the laying state of the pile frame, the included angle structure behind the pile frame is restrained not to interfere with the main deck; the maximum installation length of the upper end of the piston rod of the oil cylinder is constrained to be approximately equal when the upper end of the piston rod of the oil cylinder is hinged to the second upper hinge point of the oil cylinder and when the upper end of the piston rod of the oil cylinder is hinged to the first upper hinge point of the oil cylinder; the minimum installation length of the upper end of the piston rod of the oil cylinder when the upper end of the piston rod of the oil cylinder is hinged to the second upper hinge point of the oil cylinder is constrained to be approximately equal to the minimum installation length of the upper end of the piston rod of the oil cylinder when the upper end of the piston rod of the oil cylinder is hinged to the first upper hinge point of the oil cylinder; the structure of the oil cylinder is restrained; and inputting the objective function and the constraint condition into excell software to calculate the stress of the oil cylinder. The invention can conveniently find the arrangement sizes of the pile frame and the amplitude-variable oil cylinder when the amplitude-variable oil cylinder is better stressed without software programming.

Description

Stress optimization method for variable-amplitude oil cylinder of ultra-large pile driving barge
Technical Field
The invention relates to a stress optimization method for a luffing cylinder of an ultra-large piling ship.
Background
The luffing cylinder is a key device of the pile frame type pile driving ship, and not only relates to the use safety of the ship, but also optimizes the stress of the luffing cylinder because the manufacturing cost of the cylinder is very expensive and the reasonable formulation of parameters is the key for controlling the cost, and is very important for improving the safety of the device and reducing the purchase cost of the device. At present, no effective theoretical optimization calculation method for the stress of the luffing cylinder exists, the stress is generally obtained by calculation through repeated adjustment, and then the maximum tensile force and the maximum thrust force of the luffing cylinder are selected according to 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 a luffing cylinder of an ultra-large pile driving barge, which can conveniently find the arrangement sizes of a pile frame and the luffing cylinder when the luffing cylinder is stressed better without complicated software programming, and provide reliable theoretical guidance for optimizing the stress of the luffing cylinder and the arrangement size of the pile frame.
The purpose of the invention is realized as follows: a stress optimization method for a variable-amplitude oil cylinder of an ultra-large pile driving barge comprises the following steps:
step one, determining design variables, comprising:
horizontal distance L from lower hinge point of oil cylinder to lower hinge point of pile frame1Rightwards is + and leftwards is-;
horizontal distance L from first upper hinge point of oil cylinder to lower hinge point of pile frame2Rightwards is + and leftwards is-;
horizontal distance L from second upper hinge point of oil cylinder to lower hinge point of pile frame3Rightwards is + and leftwards is-;
vertical distance h from lower hinge point of oil cylinder to lower hinge point of pile frame1Upward is +, leftward is-;
vertical distance h from first upper hinge point of oil cylinder to lower hinge point of pile frame2Upward is +, leftward is-;
vertical distance h from second upper hinge point of oil cylinder to lower hinge point of pile frame3Upward is +, leftward is-;
the included angle a between the pile frame and the vertical direction is clockwise plus or anticlockwise;
inputting the design variables into Excel software;
determining a target function, and taking the maximum pulling force and the maximum pushing force of the amplitude-variable oil cylinder as the target function; the maximum tensile force of the variable amplitude oil cylinder occurs in the working condition of the maximum pile frame bending, and the upper end of a piston rod of the variable amplitude oil cylinder is hinged to a first upper hinge point of the oil cylinder; the maximum thrust of the amplitude-variable oil cylinder occurs in the working condition of starting to pile up the pile frame, and 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; the following two calculation formulas of the stress of the luffing cylinder are obtained according to the static balance relationship and the geometric relationship of the arrangement sizes of the pile frame and the luffing cylinder:
1) when the upper end of a piston rod of the amplitude-variable oil cylinder is hinged to a first upper hinge point of the oil cylinder, the used maximum tension F is calculated by the following formula:
Figure BDA0002940107570000021
recording as follows: f ═ F (L)1，L2，h1，h2，a)
2) 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, the maximum thrust F is used1Calculated by the following formula:
Figure BDA0002940107570000022
recording as follows: f1＝f(L1，L3，h1，h3，a)
Of the two formulas:
Figure BDA0002940107570000023
in the formula:
Figure BDA0002940107570000024
to design the coefficients; mOil cylinderThe moment is generated by the variable amplitude oil cylinder to the lower hinge point of the pile frame; mPile frameThe moment is generated by the pile frame to the lower hinge point of the pile frame; mPile and its making methodThe moment is generated by the pile to the lower hinge point of the pile frame; mHammerThe moment is generated by the pile hammer to the lower hinge point of the pile frame; mHookThe moment is generated by the lower hinge point of the pile frame by the lifting hook;
Figure BDA0002940107570000025
in the formula: g is the weight of the pile frame, and Gx and Gy are coordinates of the gravity center of the pile frame in the upright state of the pile frame by taking a lower hinge point of the pile frame as an original point;
2) the moment generated by the pile to the lower hinge point of the pile frame is calculated by the following formula:
Figure BDA0002940107570000026
in the formula: g1Is the weight of the pile, Gx1，Gy1The coordinates are the gravity center of the pile in the upright state of the pile frame and the coordinates with the lower hinge point of the pile frame as the original point;
3) the moment generated by the pile hammer to the lower hinge point of the pile frame is calculated by the following formula:
Figure BDA0002940107570000027
in the formula: g2Weight of the pile hammer, Gx2，Gy2The center of gravity of the pile hammer in the upright state of the pile frame takes the lower hinge point of the pile frame as the coordinate of the original point;
4) the moment generated by the lifting hook to the lower hinge point of the pile frame is calculated by the following formula:
Figure BDA0002940107570000031
in the formula: g3Is the weight of the hook, Gx3，Gy3The center of gravity of the lifting hook takes the lower hinge point of the pile frame as the coordinate of the original point when the pile frame is in an upright state;
step four, determining constraint conditions, including:
(1) the pile frame has an included angle a with the vertical direction when the pile frame is in a laying state0When the pile frame rear included angle structure is restrained, the included angle structure does not interfere with the main deck, namely the distance from the bottom of the included angle structure to the main deck is R1：
Figure BDA0002940107570000032
In the formula: delta h is a 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 post 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 when the upper end of the piston rod of the amplitude-variable oil cylinder is hinged to the second upper hinge point of the oil cylinder is constrained to be approximately equal to the maximum installation length Lmax when the upper end of the piston rod of the amplitude-variable oil cylinder is hinged to the first upper hinge point of the oil cylinder within 200mm of the maximum installation length Lmax;
the installation length of the piston rod of the amplitude-variable oil cylinder when the upper end of the piston rod is hinged to the second upper hinge point of the oil cylinder is as follows:
Figure BDA0002940107570000033
the installation length of the piston rod of the amplitude-variable oil cylinder when the upper end of the piston rod is hinged on the first upper hinge point of the oil cylinder is as follows:
Figure BDA0002940107570000034
namely: l ismax≈L’max
(3) The minimum installation length L' min when the upper end of the piston rod of the amplitude variation oil cylinder is hinged to the second upper hinge point of the oil cylinder is constrained to be approximately equal to the minimum installation length Lmin when the upper end of the piston rod of the amplitude variation oil cylinder is hinged to the first upper hinge point of the oil cylinder within 200mm of the minimum installation length Lmin;
namely Lmin≈L’min
(4) The structure of the amplitude variation oil cylinder is restrained, namely the difference between the minimum installation length of the amplitude variation oil cylinder and the stroke of the amplitude variation oil cylinder is not less than a set value C; the maximum installation length of the amplitude variation oil cylinder and the minimum installation length of the amplitude variation oil cylinder both consider the design allowance delta S, and the stroke S of the amplitude variation oil cylinder is calculated by the following formula:
S＝(Max{Lmax，L'max}+Δs)-(Min{Lmin，L’min}-Δs)
＝Max{Lmax，L'max}-Min{Lmin，L’min}+2Δs
the difference between the minimum installation length of the amplitude variation oil cylinder and the stroke of the amplitude variation oil cylinder is not less than a set value C:
(Min{Lmin，L’min}-Δs)-S≥C
namely: 2Min { Lmin，L’min}-Max{Lmax，L'max}-3Δs≥C
And fifthly, inputting the objective function and the constraint condition into Excel software to perform stress optimization calculation of the luffing cylinder.
In the stress optimization method for the luffing cylinder of the ultra-large pile driving vessel, the stress optimization calculation of the luffing cylinder is specifically performed by adopting the following method in the fifth step:
1) a single design variable research method is adopted, namely, the relation between the stress of the amplitude-variable oil cylinder and the design variable is researched under the condition that one of the design variables is taken as a research object and the other design variables are taken as given values; discretizing the design variable on the values, calculating the stress of the amplitude variation oil cylinder corresponding to each value, and sorting the stress into a table or a chart, wherein the influence of the stress of the amplitude variation oil cylinder on different values of the design variable is seen from the table or the chart;
2) according to the influence of each design variable value on the stress of the variable-amplitude oil cylinder in each unit change, primary and secondary sequencing is carried out on the design variables to obtain the maximum thrust of the variable-amplitude oil cylinder from the lower hinge point of the oil cylinder to the pileHorizontal distance L of hinge point under frame1The vertical distance h from the lower hinge point of the oil cylinder to the lower hinge point of the pile frame1(ii) a The maximum tension of the variable-amplitude oil cylinder is influenced by the horizontal distance L from the lower hinge point of the oil cylinder to the lower hinge point of the pile frame1The maximum influence is achieved, and the horizontal distance L from the first upper hinge point of the oil cylinder to the lower hinge point of the pile frame is2Other variables have little influence on the stress of the variable amplitude oil cylinder;
3) during optimization calculation, the design variables are sequentially valued from the primary to the secondary, namely, the numerical value of the primary design variable is determined firstly, and then the numerical value of the secondary design variable is determined according to the constraint condition, so that the optimized stress of the variable amplitude oil cylinder can be obtained.
The stress optimization method of the variable-amplitude oil cylinder of the ultra-large pile driving barge has the following characteristics: the layout sizes of the pile frame and the amplitude-variable oil cylinder when the amplitude-variable oil cylinder is stressed well can be conveniently found by simply calculating through the Excel software without complicated software programming and only editing all parameters and formulas into the Excel software, so that reliable theoretical guidance is provided for optimizing the stress of the amplitude-variable oil cylinder and the layout size of the pile frame, the compactness and the stability of the layout structures of the pile frame and the amplitude-variable oil cylinder are increased, and the service life of the amplitude-variable oil cylinder is prolonged.
Drawings
Fig. 1 is a schematic structural diagram (in four states) of the positional relationship between a pile frame and a luffing cylinder of the ultra-large pile driving barge according to the invention;
FIG. 2 is a simplified diagram of the position relationship between the pile frame and the luffing cylinder of the ultra-large pile driving barge (before the luffing cylinder is hinged);
fig. 3 is a simplified diagram of the position relationship between the pile frame and the luffing cylinder of the ultra-large pile driving barge according to the invention (after the luffing cylinder is hinged).
Detailed Description
The invention will be further explained with reference to the drawings.
Referring to fig. 1 to 3, the method for optimizing the stress of the luffing cylinder of the ultra-large piling barge according to the present invention includes the following steps:
determining design variables including the structures of all pile frames 200 influencing the stress of the amplitude-variable oil cylinder 100 and the arrangement positions of the lower hinge point of the oil cylinder and the upper hinge points of the two oil cylinders; the design variables include:
horizontal distance L from lower hinge point 10 of oil cylinder to lower hinge point 20 of pile frame1Rightwards is + and leftwards is-;
horizontal distance L from first upper hinge point 11 of oil cylinder to lower hinge point 20 of pile frame2Rightwards is + and leftwards is-;
horizontal distance L from second upper hinge point 12 of oil cylinder to lower hinge point 20 of pile frame3Rightwards is + and leftwards is-;
vertical distance h from lower hinge point 10 of oil cylinder to lower hinge point 20 of pile frame1Upward is +, leftward is-;
vertical distance h from first upper hinge point 11 of oil cylinder to lower hinge point 20 of pile frame2Upward is +, leftward is-;
vertical distance h from second upper hinge point 12 of oil cylinder to lower hinge point 20 of pile frame3Upward is +, leftward is-;
the included angle a between the pile frame 200 and the vertical direction is clockwise + and anticlockwise-;
inputting all the design variables into Excel software;
determining a target function, and taking the maximum pulling force and the maximum pushing force of the amplitude-variable oil cylinder as the target function; the maximum pulling force of the amplitude-variable oil cylinder 100 is in the maximum pile frame pitching working condition, at the moment, a pile load exists, 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 amplitude-variable oil cylinder 100 is hinged to a first upper hinge point 11 (see figure 2) of the oil cylinder; the maximum thrust of the luffing cylinder 100 occurs in the working condition of starting pile frame lifting, and the upper end of the piston rod of the luffing cylinder 100 is hinged to the second upper hinge point 12 of the cylinder (see fig. 3); the following two calculation formulas of the stress of the luffing cylinder are obtained according to the static balance relationship and the geometric relationship of the arrangement sizes of the pile frame 200 and the luffing cylinder 100:
1) when the upper end of the piston rod of the amplitude-variable oil cylinder 100 is hinged to the first upper hinge point 11 of the oil cylinder, the maximum pulling force F is calculated by the following formula:
Figure BDA0002940107570000051
recording as follows: f ═ F (L)1，L2，h1，h2，a)
2) When the upper end of the piston rod of the amplitude-variable oil cylinder 100 is hinged at the second upper hinge point 12 of the oil cylinder, the maximum thrust F is used1Calculated by the following formula:
Figure BDA0002940107570000061
recording as follows: f1＝f(L1，L3，h1，h3，a)
Of the two formulas:
Figure BDA0002940107570000062
in the formula:
Figure BDA0002940107570000063
to design the coefficients; mOil cylinderThe moment is generated by the amplitude-variable oil cylinder 100 to the lower hinge point 20 of the pile frame; mPile frameThe moment generated by the pile frame 200 to the pile frame lower hinge point 20; mPile and its making methodThe moment generated by the pile to the pile frame lower hinge point 20; mHammerThe moment generated by the pile hammer to the lower hinge point 20 of the pile frame; mHookThe moment generated by the lifting hook to the pile frame lower hinge point 20;
the pile driving boat adopts the amplitude-variable oil cylinder 100 to drive the pile frame 200 to change amplitude, and when the pile frame works, the moment generated by the pile frame, the pile hammer and the lifting hook to the lower hinge point 20 of the pile frame due to self weight is balanced by the moment of the amplitude-variable oil cylinder 100 to the lower hinge point 20 of the pile frame;
Figure BDA0002940107570000064
in the formula: g is the weight of the pile frame, and Gx and Gy are coordinates of the gravity center of the pile frame in the upright state of the pile frame by taking a lower hinge point of the pile frame as an original point;
2) the moment generated by the pile to the lower hinge point of the pile frame is calculated by the following formula:
Figure BDA0002940107570000065
in the formula: g1Is the weight of the pile, Gx1，Gy1The coordinates are the gravity center of the pile in the upright state of the pile frame and the coordinates with the lower hinge point of the pile frame as the original point;
3) the moment generated by the pile hammer to the lower hinge point of the pile frame is calculated by the following formula:
Figure BDA0002940107570000066
in the formula: g2Weight of the pile hammer, Gx2，Gy2The center of gravity of the pile hammer in the upright state of the pile frame takes the lower hinge point of the pile frame as the coordinate of the original point;
4) the moment generated by the lifting hook to the lower hinge point of the pile frame is calculated by the following formula:
Figure BDA0002940107570000067
in the formula: g3Is the weight of the hook, Gx3，Gy3The center of gravity of the lifting hook takes the lower hinge point of the pile frame as the coordinate of the original point when the pile frame is in an upright state;
step four, determining constraint conditions, including the following four constraint conditions:
(1) when the pile frame 200 is in a laying state, the included angle between the pile frame 200 and the vertical direction is a0In the meantime, the post frame rear included angle restraining structure 201 does not interfere with the main deck 30, that is, the distance from the bottom of the post frame rear included angle restraining structure 201 to the main deck 30 is R1：
Figure BDA0002940107570000071
In the formula: delta h is a 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 post frame rear included angle structure 201; h is the distance from the lower hinge point 10 of the oil cylinder to the main deck 30;
(2) the maximum installation length L' max when the upper end of the piston rod of the amplitude-variable oil cylinder is hinged to the second upper hinge point of the oil cylinder is constrained to be approximately equal to the maximum installation length Lmax when the upper end of the piston rod of the amplitude-variable oil cylinder is hinged to the first upper hinge point of the oil cylinder within 200mm of the maximum installation length Lmax;
the installation length of the piston rod of the amplitude-variable oil cylinder when the upper end of the piston rod is hinged to the second upper hinge point of the oil cylinder is as follows:
Figure BDA0002940107570000072
the installation length of the piston rod of the amplitude-variable oil cylinder when the upper end of the piston rod is hinged on the first upper hinge point of the oil cylinder is as follows:
Figure BDA0002940107570000073
namely: l ismax≈L’max
(3) The minimum installation length L' min when the upper end of the piston rod of the amplitude variation oil cylinder is hinged to the second upper hinge point of the oil cylinder is constrained to be approximately equal to the minimum installation length Lmin when the upper end of the piston rod of the amplitude variation oil cylinder is hinged to the first upper hinge point of the oil cylinder within 200mm of the minimum installation length Lmin;
namely Lmin≈L’min
(4) The structure of the amplitude variation oil cylinder is restrained, namely the difference between the minimum installation length of the amplitude variation oil cylinder and the stroke of the amplitude variation oil cylinder is not less than a set value C; the maximum installation length of the amplitude variation oil cylinder and the minimum installation length of the amplitude variation oil cylinder both consider the design allowance delta S, and the stroke S of the amplitude variation oil cylinder is calculated by the following formula:
S＝(Max{Lmax，L'max}+Δs)-(Min{Lmin，L’min}-Δs)
＝Max{Lmax，L'max}-Min{Lmin，L’min}+2Δs
the difference between the minimum installation length of the amplitude variation oil cylinder and the stroke of the amplitude variation oil cylinder is not less than a set value C:
(Min{Lmin，L’min}-Δs)-S≥C
namely: 2Min { Lmin，L’min}-Max{Lmax，L'max}-3Δs≥C
Inputting the objective function and the constraint condition into Excel software to perform stress optimization calculation of the luffing cylinder, and specifically performing the following steps:
1) a single design variable research method is adopted, namely, the relation between the stress of the amplitude-variable oil cylinder and the design variable is researched under the condition that one of the design variables is taken as a research object and the other design variables are taken as given values; discretizing the design variable on the values, calculating the stress of the amplitude variation oil cylinder corresponding to each value, and sorting the stress into a table or a chart, wherein the influence of the stress of the amplitude variation oil cylinder on different values of the design variable is seen from the table or the chart;
2) according to the stress influence on the variable-amplitude oil cylinder when each unit of variable value of each design variable changes, the design variables are subjected to primary and secondary sequencing to obtain the horizontal distance L from the lower hinge point of the oil cylinder to the lower hinge point of the pile frame, which is the maximum thrust of the variable-amplitude oil cylinder1The vertical distance h from the lower hinge point of the oil cylinder to the lower hinge point of the pile frame1(ii) a The maximum tension of the variable-amplitude oil cylinder is influenced by the horizontal distance L from the lower hinge point of the oil cylinder to the lower hinge point of the pile frame1The maximum influence is achieved, and the horizontal distance L from the first upper hinge point of the oil cylinder to the lower hinge point of the pile frame is2Other variables have little influence on the stress of the variable amplitude oil cylinder;
3) during optimization calculation, the design variables are sequentially valued from the primary to the secondary, namely, the numerical value of the primary design variable is determined firstly, and then the numerical value of the secondary design variable is determined according to the constraint condition, so that the optimized stress of the variable amplitude oil cylinder can be obtained.
The invention will now be described by taking a 133 m ultra-large pile driving vessel as an example:
first, input the parameter
1. Input design variables
Horizontal distance L from lower hinge point 10 of oil cylinder to lower hinge point 20 of pile frame1Vertical distance from oil cylinder lower hinge point 10 to pile frame lower hinge point 20 being-17700 mmh1The horizontal distance L from the first upper hinge point 11 of the oil cylinder to the lower hinge point 20 of the pile frame is-8700 mm2Vertical distance h from first upper hinge point 11 of oil cylinder to lower hinge point 20 of pile frame219000mm, the horizontal distance L from the second upper hinge point 12 of the oil cylinder to the lower hinge point 20 of the pile frame3The vertical distance h from the second upper hinge point 12 of the oil cylinder to the lower hinge point 20 of the pile frame is-1820 mm3＝28910mm。
2. Inputting parameters for calculating torque
Weight G of pile frame, gravity center coordinates Gx and Gy of pile frame, and weight G of pile1Center of gravity Gx of pile1、Gy1Weight of hammer G2Gravity center coordinates Gx of hammer2、Gy2Weight of hook G3Gravity center coordinate Gx of lifting hook3、Gy3The values of (A) are as follows:
G＝840t，Gx＝-2300mm，Gy＝47000mm；
G1＝300t，Gx1＝3530mm，Gy137100mm, G is taken when the pile is not being driven1＝0；
G2＝280t，Gx2＝3530mm，Gy2When the pile frame is placed under the working condition, the gravity center coordinate of the pile hammer is considered according to the position of the hinge-changing cross beam, namely Gy is taken2＝h2；
G3＝60t，Gx3＝3530mm，Gy3When the pile frame is placed under the working condition of 91950mm, the lifting hook is positioned at the position of the sealing hook on the hinge changing beam, Gx3 is 0, and Gy3 is h 2;
the value of an included angle a between the pile frame and the vertical direction is as follows:
under the working condition of maximum tension: a is 14 °; under the working condition of maximum thrust: a is-70.5 °; when the amplitude-variable oil cylinder changes the hinge: a is-27 °; when the pile frame is maximally inclined forwards: a is 22 °.
3. Inputting design coefficient for calculating stress of amplitude variation oil cylinder
Figure BDA0002940107570000091
Under the working condition of maximum tension:
Figure BDA0002940107570000092
under the working condition of maximum thrust:
Figure BDA0002940107570000093
secondly, calculating the maximum tension F of the luffing cylinder under the working condition of the maximum pitching pile frame, wherein the upper end of a piston rod of the luffing cylinder 100 is hinged to a first upper hinge point 11 of the cylinder, and an included angle a between the pile frame 200 and the vertical direction is 14 degrees;
calculating the moment M generated by the pile frame to the lower hinge point of the pile frame in Excel softwarePile frame：
Figure BDA0002940107570000094
Calculating the moment M generated by the pile to the lower hinge point of the pile frame in Excel software according to the following formulaPile and its making method：
Figure BDA0002940107570000095
Calculating the moment M generated by the lower hinge point of the pile frame by the hammer in Excel software according to the following formulaHammer：
Figure BDA0002940107570000096
Calculating the moment M generated by the lower hinge point of the pile frame by the lifting hook in Excel software according to the following formulaHook：
Figure BDA0002940107570000097
Calculating the moment M generated by the luffing oil cylinder to the lower hinge point of the pile frame in Excel software according to the following formulaOil cylinder：
Figure BDA0002940107570000098
Calculating the installation length L of the luffing oil cylinder in Excel software according to the following formula:
Figure BDA0002940107570000099
calculating the maximum tensile force F of the amplitude-variable oil cylinder in Excel software according to the following formula:
Figure BDA00029401075700000910
thirdly, calculating the maximum thrust F of the luffing cylinder under the working condition of starting to pile up the pile frame1At the moment, the upper end of a piston rod of the amplitude-variable oil cylinder 100 is hinged to a second upper hinge point 12 of the oil cylinder, and an included angle a between the pile frame 200 and the vertical direction is-70.5 degrees;
calculating the moment M generated by the pile frame to the lower hinge point of the pile frame in Excel software according to the following formulaPile frame：
Figure BDA00029401075700000911
Calculating the moment M generated by the pile to the lower hinge point of the pile frame in Excel software according to the following formulaPile and its making method：
Figure BDA00029401075700000912
Calculating the moment M generated by the lower hinge point of the pile frame by the hammer in Excel software according to the following formulaHammer：
Figure BDA0002940107570000101
Calculating the moment M generated by the lower hinge point of the pile frame by the lifting hook in Excel software according to the following formulaHook：
Figure BDA0002940107570000102
Calculating the moment M generated by the luffing oil cylinder to the lower hinge point of the pile frame in Excel software according to the following formulaOil cylinder：
Figure BDA0002940107570000103
Calculating the installation length L' of the luffing cylinder in Excel software according to the following formula:
Figure BDA0002940107570000104
calculating the maximum thrust F of the luffing oil cylinder in Excel software according to the following formula1：
Figure BDA0002940107570000105
Fourthly, editing a calculation formula of the four constraint conditions in Excel software, and judging whether the value of the design variable meets the constraint conditions or not;
constraint (1): when the pile frame is placed, the included angle a between the pile frame and the vertical direction0The distance between the lower hinge point of the oil cylinder and the main deck is 1100mm, the set safe height delta h from the bottom of the post frame rear included angle structure to the main deck is 300mm, namely the height R from the bottom of the post frame rear included angle structure to the main deck1Calculated from the following formula:
Figure BDA0002940107570000106
constraint (2): maximum installation length of variable amplitude oil cylinder
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, an included angle a between the pile frame and the vertical direction when the corresponding amplitude-variable oil cylinder is hinged is-27 degrees, and the maximum installation length of the amplitude-variable oil cylinder is calculated by the following formula:
Figure BDA0002940107570000107
when the upper end of a piston rod of the amplitude-variable oil cylinder is hinged to a first upper hinge point of the oil cylinder, an included angle a between the pile frame and the vertical direction is 22 degrees when the corresponding pile frame is maximally inclined forwards, and the maximum installation length of the amplitude-variable oil cylinder is calculated by the following formula:
Figure BDA0002940107570000108
lmax is 33737.31(mm), L' max is 33762.17(mm), the difference is 24.86, and the constraint is approximately equal within 200mm, namely Lmax(a＝22)≈L’max(a＝-27)
Constraint (3): minimum installation length of variable amplitude oil cylinder
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, an included angle a between the pile frame and the vertical direction when the corresponding pile frame is placed is-70.5 degrees, and the minimum installation length of the amplitude-variable oil cylinder is calculated by the following formula:
Figure BDA0002940107570000111
when the upper end of a piston rod of the amplitude-variable oil cylinder is hinged to a first upper hinge point of the oil cylinder, an included angle a between a pile frame and the vertical direction when the corresponding amplitude-variable oil cylinder is hinged is-27 degrees, and the minimum installation length of the amplitude-variable oil cylinder is calculated by the following formula:
Figure BDA0002940107570000112
the Lmin is 19352.13(mm), the L' min is 19491.69(mm), the difference is 139.56, and the constraint is approximately equal when the difference is within 200 mm; namely:
Lmin(a＝-27)≈L’min(a＝-70.5)
constraint (4): the difference between the minimum installation length of the amplitude variation oil cylinder and the stroke of the amplitude variation oil cylinder is not less than a set value C, the value C is determined according to the design requirements of different oil cylinder manufacturers, C is 4200mm in the embodiment, and the design allowance delta s of the maximum installation length and the minimum installation length of the amplitude variation oil cylinder is 200mm, namely
2Min{Lmin，L’min}-Max{Lmax，L'max)}＝4942.092342≥4800
And fifthly, a single design variable research method is adopted, namely, the relation between the stress of the variable amplitude oil cylinder and the design variable is researched under the condition that one of the design variables is taken as a research object and the other design variables are given values. Discretizing the design variable on the values, calculating the stress of the amplitude variation oil cylinder corresponding to each value, and sorting the stress into a table or a chart, so that the influence of the stress of the amplitude variation oil cylinder on different values of the design variable can be visually seen. In order to facilitate data analysis, other design variables are processed according to the finally adopted numerical values of the pile driving barge, so that the judgment of the variation trend of each design variable on the stress of 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 researched1When the force variation relation with the amplitude variation oil cylinder is satisfied, h1，L2，h2，L3And h3Setting according to the data; on the premise that the second upper hinge point of the oil cylinder meets the end size of the piston rod of the variable-amplitude oil cylinder, the closer to the front chord of the pile frame, the more favorable the structural design is, so that L3The value of (A) has small influence change on the stress of the luffing cylinder and can not be analyzed.
Sorting the calculation results into tables 1 to 5; in the table, ok indicates that the constraint is correct, and error indicates that the constraint is wrong.
Table 1 shows the maximum stress and the maximum tensile force of the luffing cylinder and L1In relation to (2)
Figure BDA0002940107570000113
Figure BDA0002940107570000121
Table 2 shows the maximum stress and the maximum tensile force of the variable amplitude oil cylinder and h1In relation to (2)
h1，mm Maximum tensile force, 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 thrust and the maximum tension of the variable amplitude oil cylinder and L2In relation to (2)
L2，mm Maximum tensile force, 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 thrust and the maximum tension of the variable amplitude oil cylinder and h2In relation to (2)
h2，mm Maximum tensile force, 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 thrust and the maximum tension of the variable amplitude oil cylinder and h3In relation to (2)
Figure BDA0002940107570000122
Figure BDA0002940107570000131
Sixthly, stress optimization analysis and conclusion of variable amplitude 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 frame1The maximum thrust and the maximum tension of the variable amplitude oil cylinder are influenced most obviously, and the variable amplitude oilThe maximum pushing force and the maximum pulling force of the cylinder follow L1Is increased and decreased. Preferentially determining L for point selection of variable amplitude oil cylinder1(ii) a On the premise of meeting other constraint conditions, L1The 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 frame2The maximum thrust of the amplitude variation oil cylinder is irrelevant, the maximum tension of the amplitude variation oil cylinder is only relevant, and the maximum tension of the amplitude variation oil cylinder follows L2Increase and decrease; at the same time, the L2The increase can also increase the overall maximum bending section modulus of the pile frame structure, so that the L value meets the constraint condition2The value should be as large as possible.
C) Vertical distance h from lower hinge point of oil cylinder to lower hinge point of pile frame1The maximum tensile force of the amplitude variation oil cylinder is slightly influenced, and the maximum thrust of the amplitude variation oil cylinder is influenced to a certain extent, h1The larger the value is, the smaller the maximum thrust of the luffing cylinder is, but the larger the height of the pile frame after being laid down is, and the navigation height of the ship 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 reduced1The value of (a).
D) Vertical distance h from first upper hinge point of oil cylinder to lower hinge point of pile frame2And the vertical distance h from the second upper hinge point of the oil cylinder to the lower hinge point of the pile frame3The value of (a) has less influence on the stress of the luffing cylinder, mainly influences the maximum installation distance and the minimum installation distance of the luffing cylinder, and the installation distance of the luffing cylinder is along with h2And h3The increase is obviously increased, but the theoretical stroke change of the amplitude variation oil cylinder is not large; the increase of the installation distance of the luffing cylinder means that the effective stroke of the luffing cylinder is not fully utilized, which will cause unnecessary cost increase.
E) According to the analysis, selecting the horizontal distance L from the lower hinge point of the oil cylinder to the lower hinge point of the pile frame117700mm, vertical distance h from lower hinge point of oil cylinder to lower hinge point of pile frame1The horizontal distance L from the first upper hinge point of the oil cylinder to the lower hinge point of the pile frame is-8700 mm2Vertical distance h from first upper hinge point of oil cylinder to lower hinge point of pile frame219000mm, the horizontal distance from the second upper hinge point of the oil cylinder to the lower hinge point of the pile frameIs far from L3Equal to-1820 mm, the vertical distance h from the second upper hinge point of the oil cylinder to the lower hinge point of the pile frame328910mm is a reasonable value, and the purpose of optimizing the stress of the luffing cylinder is basically achieved.
According to the stress optimization method of the luffing cylinder of the ultra-large pile driving vessel, complicated software programming is not needed, only calculation formulas of all design variables and constraint conditions and calculation formulas of the objective function are edited into Excel software, and the arrangement sizes of the pile frame and the luffing cylinder can be conveniently found through simple calculation of the Excel software, so that reliable theoretical guidance is provided for optimizing the stress of the luffing cylinder and the arrangement sizes of the pile frame, the compactness and the stability of the arrangement structure of the pile frame and the luffing cylinder are increased, and the service life of the luffing cylinder is prolonged.
The above embodiments are provided only for illustrating the present invention and not for limiting the present invention, and those skilled in the art can make various changes and modifications without departing from the spirit and scope of the present invention, and therefore all equivalent technical solutions should also fall within the scope of the present invention, and should be defined by the claims.

Claims (2)

1. A stress optimization method for a variable amplitude oil cylinder of an ultra-large piling ship is characterized by comprising the following steps:
step one, determining design variables, comprising:
horizontal distance L from lower hinge point of oil cylinder to lower hinge point of pile frame1Rightwards is + and leftwards is-;
horizontal distance L from first upper hinge point of oil cylinder to lower hinge point of pile frame2Rightwards is + and leftwards is-;
horizontal distance L from second upper hinge point of oil cylinder to lower hinge point of pile frame3Rightwards is + and leftwards is-;
vertical distance h from lower hinge point of oil cylinder to lower hinge point of pile frame1Upward is +, leftward is-;
vertical distance h from first upper hinge point of oil cylinder to lower hinge point of pile frame2Upward is +, leftward is-;
oil cylinderVertical distance h from second upper hinge point to pile frame lower hinge point3Upward is +, leftward is-;
the included angle a between the pile frame and the vertical direction is clockwise plus or anticlockwise;
inputting the design variables into Excel software;
determining a target function, and taking the maximum pulling force and the maximum pushing force of the amplitude-variable oil cylinder as the target function; the maximum tensile force of the variable amplitude oil cylinder occurs in the working condition of the maximum pile frame bending, and the upper end of a piston rod of the variable amplitude oil cylinder is hinged to a first upper hinge point of the oil cylinder; the maximum thrust of the amplitude-variable oil cylinder occurs in the working condition of starting to pile up the pile frame, and 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; the following two calculation formulas of the stress of the luffing cylinder are obtained according to the static balance relationship and the geometric relationship of the arrangement sizes of the pile frame and the luffing cylinder:
1) when the upper end of a piston rod of the amplitude-variable oil cylinder is hinged to a first upper hinge point of the oil cylinder, the used maximum tension F is calculated by the following formula:
Figure FDA0002940107560000011
recording as follows: f ═ F (L)1，L2，h1，h2，a)
2) 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, the maximum thrust F is used1Calculated by the following formula:
Figure FDA0002940107560000012
recording as follows: f1＝f(L1，L3，h1，h3，a)
Of the two formulas:
Figure FDA0002940107560000013
in the formula:
Figure FDA0002940107560000014
to design the coefficients; mOil cylinderThe moment is generated by the variable amplitude oil cylinder to the lower hinge point of the pile frame; mPile frameThe moment is generated by the pile frame to the lower hinge point of the pile frame; mPile and its making methodThe moment is generated by the pile to the lower hinge point of the pile frame; mHammerThe moment is generated by the pile hammer to the lower hinge point of the pile frame; mHookThe moment is generated by the lower hinge point of the pile frame by the lifting hook;
Figure FDA0002940107560000021
in the formula: g is the weight of the pile frame, and Gx and Gy are coordinates of the gravity center of the pile frame in the upright state of the pile frame by taking a lower hinge point of the pile frame as an original point;
2) the moment generated by the pile to the lower hinge point of the pile frame is calculated by the following formula:
Figure FDA0002940107560000022
in the formula: g1Is the weight of the pile, Gx1，Gy1The coordinates are the gravity center of the pile in the upright state of the pile frame and the coordinates with the lower hinge point of the pile frame as the original point;
3) the moment generated by the pile hammer to the lower hinge point of the pile frame is calculated by the following formula:
Figure FDA0002940107560000023
in the formula: g2Weight of the pile hammer, Gx2，Gy2The center of gravity of the pile hammer in the upright state of the pile frame takes the lower hinge point of the pile frame as the coordinate of the original point;
4) the moment generated by the lifting hook to the lower hinge point of the pile frame is calculated by the following formula:
Figure FDA0002940107560000024
in the formula: g3Is the weight of the hook, Gx3，Gy3The center of gravity of the lifting hook takes the lower hinge point of the pile frame as the coordinate of the original point when the pile frame is in an upright state;
step four, determining constraint conditions, including:
(1) the pile frame has an included angle a with the vertical direction when the pile frame is in a laying state0When the pile frame rear included angle structure is restrained, the included angle structure does not interfere with the main deck, namely the distance from the bottom of the included angle structure to the main deck is R1：
Figure FDA0002940107560000025
In the formula: delta h is a 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 post 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 when the upper end of the piston rod of the amplitude-variable oil cylinder is hinged to the second upper hinge point of the oil cylinder is constrained to be approximately equal to the maximum installation length Lmax when the upper end of the piston rod of the amplitude-variable oil cylinder is hinged to the first upper hinge point of the oil cylinder within 200mm of the maximum installation length Lmax;
the installation length of the piston rod of the amplitude-variable oil cylinder when the upper end of the piston rod is hinged to the second upper hinge point of the oil cylinder is as follows:
Figure FDA0002940107560000026
the installation length of the piston rod of the amplitude-variable oil cylinder when the upper end of the piston rod is hinged on the first upper hinge point of the oil cylinder is as follows:
Figure FDA0002940107560000031
namely: l ismax≈L’max
(3) The minimum installation length L' min when the upper end of the piston rod of the amplitude variation oil cylinder is hinged to the second upper hinge point of the oil cylinder is constrained to be approximately equal to the minimum installation length Lmin when the upper end of the piston rod of the amplitude variation oil cylinder is hinged to the first upper hinge point of the oil cylinder within 200mm of the minimum installation length Lmin;
namely Lmin≈L’min
(4) The structure of the amplitude variation oil cylinder is restrained, namely the difference between the minimum installation length of the amplitude variation oil cylinder and the stroke of the amplitude variation oil cylinder is not less than a set value C; the maximum installation length of the amplitude variation oil cylinder and the minimum installation length of the amplitude variation oil cylinder both consider the design allowance delta S, and the stroke S of the amplitude variation oil cylinder is calculated by the following formula:
S＝(Max{Lmax，L'max}+Δs)-(Min{Lmin，L’min}-Δs)
＝Max{Lmax，L'max}-Min{Lmin，L’min}+2Δs
the difference between the minimum installation length of the amplitude variation oil cylinder and the stroke of the amplitude variation oil cylinder is not less than a set value C:
(Min{Lmin，L’min}-Δs)-S≥C
namely: 2Min { Lmin，L’min}-Max{Lmax，L'max}-3Δs≥C
And 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 of the luffing cylinder of the ultra-large piling barge according to claim 1, wherein the stress optimization calculation of the luffing cylinder is performed by specifically adopting the following method in the step five:
1) a single design variable research method is adopted, namely, the relation between the stress of the amplitude-variable oil cylinder and the design variable is researched under the condition that one of the design variables is taken as a research object and the other design variables are taken as given values; discretizing the design variable on the values, calculating the stress of the amplitude variation oil cylinder corresponding to each value, and sorting the stress into a table or a chart, wherein the influence of the stress of the amplitude variation oil cylinder on different values of the design variable is seen from the table or the chart;
2) according to each facilityThe design variables are subjected to primary and secondary sequencing according to the stress influence on the variable-amplitude oil cylinder when the value of the measurement variable changes per unit, and the horizontal distance L from the lower hinge point of the oil cylinder to the lower hinge point of the pile frame, which is the maximum thrust of the variable-amplitude oil cylinder, is obtained1The vertical distance h from the lower hinge point of the oil cylinder to the lower hinge point of the pile frame1(ii) a The maximum tension of the variable-amplitude oil cylinder is influenced by the horizontal distance L from the lower hinge point of the oil cylinder to the lower hinge point of the pile frame1The maximum influence is achieved, and the horizontal distance L from the first upper hinge point of the oil cylinder to the lower hinge point of the pile frame is2Other variables have little influence on the stress of the variable amplitude oil cylinder;
3) during optimization calculation, the design variables are sequentially valued from the primary to the secondary, namely, the numerical value of the primary design variable is determined firstly, and then the numerical value of the secondary design variable is determined according to the constraint condition, so that the optimized stress of the variable amplitude oil cylinder can be obtained.
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