CN106986271B - Consider the marine hoist control method of lasting interference and parameter uncertainty - Google Patents
Consider the marine hoist control method of lasting interference and parameter uncertainty Download PDFInfo
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C13/00—Other constructional features or details
- B66C13/18—Control systems or devices
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
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Abstract
A kind of marine hoist control method of consideration lasting interference and parameter uncertainty, belongs to the technical field that Underactuated Mechanical Systems automatically control.This method includes:For the marine hoist system dynamics model by lasting interference effect, consider that the Parameter uncertainties including load etc. influence, a kind of nonlinear control method is devised, can realize the control targe of marine hoist, while the gravity that can compensate for during lifting rope lifting and cantilever pitching influences.The experimental results showed that the method can handle the parameter uncertainty and interference effect of marine hoist system, effectively inhibit hunting of load, realizes being accurately positioned for load.
Description
Technical field
The invention belongs to the technical fields that Underactuated Mechanical Systems automatically control, and are suitable for by sea more particularly to one kind
The load for the marine hoist system that unrestrained persistent disturbances and systematic parameter uncertainty influence is accurately positioned and disappears pendulum control.
Background technology
For a long time, sea transport due to high-throughput, low cost, transportation range length etc. advantages, in national economy
Play important role in development.Sea transport mainly realized by cargo-container ship, in the cargo handling process of container, no
Avoidable ground will use marine hoist system.Different from land-bound crane, marine hoist is due to being mounted on freighter, working environment
It is more complicated, it is more vulnerable to influence of many uncertain noises, such as wave, strong wind etc., this also substantially increases marine hoist
System automatically controls the challenge of problem.Currently, the control of marine hoist is usually by manually realizing.But at the same time, manually
There is some defects for operation, such as working efficiency is low, control accuracy is poor.Particularly, when marine hoist system context compared with
When being severe, even the worker to know a thing or two is also difficult to realize preferably control the system.Therefore, using automatically controlling skill
Art, it has been the task of top priority to design suitable and efficient autocontrol method for marine hoist system.
To crane system, including land and marine hoist system, a most important challenge is the drive lacking characteristic of system,
That is the control input number of system is less than system degree of freedom number to be controlled.Between past decades, underactuated system is asked
The research of topic has received widespread attention[1],[2].Specifically, for land-bound crane system, it has been proposed that serial of methods
Carry out the hunting of load inhibition problem during processing work, such as input shaper method[3]-[5], method for planning track[6]-[8]Equal open loops
Control method.In addition to this, better robustness, some scholars devise corresponding Closed-loop Control Strategy in order to obtain[9]-[12]。
Unlike land-bound crane system, for marine hoist system due to being fixed on hull, its pedestal is can to move
It is dynamic, at the same be more vulnerable to include the various interference such as wave, strong wind influence.In other words, marine hoist system is operated in non-
In inertial system, this is also the main distinction with land-bound crane.On the other hand, the interference that marine hoist is subject to include matching interference with
Non-matching two kinds of interference, increases the difficulty of design of control method.For these reasons, for the control method of land-bound crane without
Method is applied to marine hoist system, therefore, suitable Automatic Control Strategy is designed for marine hoist system, has theoretical and reality
Meaning, at the same it is also extremely challenging.
Although the automatic control problem of land-bound crane system has been widely studied, the research of marine hoist system control is still located
In the stage of opposing primary.So far, the control method for being directed to the system on a small quantity is only proposed.Rauh et al.[13]It proposes
A method of based on linear matrix inequality, to handle external interference, be controlled effectively result.Document [14] proposes
A kind of variable-gain observer and Gain-scheduling control rule control Maryland marine hoist system.Qian et al.[15]Propose one kind
Repetitive study control strategy, for inhibiting periodic sea wave disturbance.Document [16] proposes a kind of linear based on partial feedback
The method of change can obtain the control result of final Uniformly stable.Some control methods based on sliding formwork[17]-[19]Also by success
Ground is applied to marine hoist system, has obtained better robust control effect.In addition, the control method based on fuzzy logic[20]
It can also be used for marine hoist and obtain effective control effect.
Currently, for the control of marine hoist system, there are still some urgent problems to be solved.First, it is hung in view of peculiar to vessel
There are the pitching of cantilever and the lifting of load in vehicle system work process, need precisely to mend the gravity of cantilever and load
It repays;However, in practice, it is difficult to accurately measure cantilever quality etc.;Secondly, existing major part method is required to hang to peculiar to vessel
Vehicle system model carries out certain approximate processing, and when the condition that approximation needs cannot be satisfied, the effect of these methods may
It has a greatly reduced quality;Finally, part control method can only obtain the control result of ultimately uniform boundary, can not ensure that error convergence arrives
Zero, meanwhile, certain methods do not account for the elevating movement of load, application field relative narrower.
In conclusion for processing at present there are still these problems, obtain better marine hoist system control effect, it is anxious
Suitable autocontrol method need to be designed.
Invention content
Present invention aim to address in place of current marine hoist system control method above shortcomings, one kind is provided
Consider the marine hoist control method of lasting interference and parameter uncertainty.
This invention address that by constructing and analyzing new stored-energy function, propose a kind of novel to be directed to parameter uncertainty
Marine hoist control method, and consider lifting rope length constraint, may be implemented to unknown cantilever and load the effective compensation of gravity,
Ensure that lifting rope length is in effective range in the course of work simultaneously.This method is not necessarily to carry out approximate processing to model, and can be with
Asymptotically stable control effect is obtained, is applied to practical marine hoist platform and is tested, it can be uncertain in systematic parameter
In the case of, preferable control effect is obtained, working efficiency is improved.
The marine hoist control method of consideration lasting interference and parameter uncertainty provided by the invention:
1st, system control targe and corresponding constraint are determined
The control targe of marine hoist system includes following three part:1. in geodetic coordinatesUnder, adjust load situation
Reach its target location [ygd zgd], wherein ygd,zgdIt respectively representsThe coordinate of load target position under coordinate system;2. inhibiting
With elimination geodetic coordinatesUnder hunting of load;3. during entire control, the lifting rope length of marine hoist system, which should be in, to be had
It imitates in range, i.e.,
Lmin< L (t) < Lmax (13)
Wherein, L (t) indicates the lifting rope length of marine hoist system;T in bracket indicates the time, and (t) is indicated behind variable
The variable is that it is subsequent (t) to omit most number variable for simplicity for the function about the time;Lmin,LmaxIt indicates respectively effective
The lower limit and the upper limit of lifting rope length.
2nd, error signal and auxiliary function are defined
Introduce following coordinate transform:
Wherein, subscript T representing matrixes/vector transposition, φ (t) indicate that the pitch angle of cantilever, L (t) indicate the length of lifting rope,
θ (t) indicates that load pivot angle, ρ (t) indicate that hull roll angle caused by wave, ξ represent transformed state vector, ξ1(t),ξ2
(t),ξ3(t) system state amount after representation transformation, the t in bracket indicate the time, behind variable (t) indicate the variable be about
It is subsequent (t) to omit most number variable for simplicity for the function of time;Using above-mentioned coordinate transformation method, in conjunction with system
Control targe, the target location of quantity of state is as follows after can must converting:
Wherein, arccos indicates inverse cosine function, ygd,zgdRepresent the target location coordinate of load, LjRepresent the length of cantilever
Degree, ξ1d,ξ2d,ξ3dRespectively represent quantity of state ξ after converting1(t),ξ2(t),ξ3(t) target location.
Further, error signal e is defined1(t),e2(t),e3(t) as follows:
e1=ξ1-ξ1d,e2=ξ2-ξ2d,e3=ξ3-ξ3d=ξ3 (19)
Then error signal is about the derivative of time:
Wherein,Respectively represent ξ1(t),ξ2(t),ξ3(t) about the derivative of time.Define auxiliary function
γ1(e1),γ2(e2),γ3(ξ3) as follows:
Wherein,Indicate positive parameter, function s (*'s) is defined as follows:
Wherein, the independent variable of * representative functions s (*).
3rd, control law determines
Design cantilever pitch moment um(t) and lifting rope tractive force uf(t) control law is as follows:
Wherein,For positive control gain.
4th, control method is realized
Using the sensor on marine hoist, the pitch angle φ (t) and angular speed of cantilever are measuredThe length L of lifting rope
(t) and long change of rope speedHull roll angle ρ (t) and its angular speedUsing formula (24), control is calculated in real time
Signal, for controlling corresponding driving motor, realization accurately controls marine hoist system.
The theoretical foundation and derivation of the method for the present invention:
1st, system model
For marine hoist system, useRespectively represent earth coordinates and hull coordinate system.zgAxis and ygAxis
It is respectively perpendicular to and is parallel to ground level.zsAxis and ysAxis is respectively perpendicular to and is parallel to boat body plane.Utilize Lagrange
Method, the kinetic model for obtaining marine hoist system are as follows:
Wherein, φ (t), L (t), θ (t) indicate cantilever pitch angle, lifting rope length and load pivot angle respectively,
Indicate cantilever rate of pitch and angular acceleration,The speed and acceleration of long change of rope are represented,It is negative
Pivot angle angular speed is carried,To load pivot angle angular acceleration;T indicates the time, and (t) indicates that the variable is about the time behind variable
Function in the case where not producing ambiguity, (t) in most of variable is omitted in subsequent formula for simplicity;
mc,md,LjRespectively indicate load quality, cantilever barycenter-pitching shaft distance and cantilever quality product and jib-length;J
Cantilever rotary inertia is represented, g is acceleration of gravity;Cθ-φ,Sθ-φ,Cφ-ρ,Cθ-ρ,Sθ-ρIt is defined as follows:
Cθ-φ=cos (θ-φ), Sθ-φ=sin (θ-φ), Cφ-ρ=cos (φ-ρ), Cθ-ρ=cos (θ-ρ), Sθ-ρ=sin
(θ-ρ)
ρ(t),Represent hull roll angle and corresponding angular speed, angular acceleration;um(t),uf(t) it indicates respectively
Cantilever torque and lifting rope tractive force, fd1(t),fd2(t),fd3(t) external interference is represented, concrete form is as follows:
Wherein, c is resistance dependent constant.
Kinetic model (1)-(3) are rewritten into matrix form, it is specific as follows:
Wherein, q=[φ L θ]TFor system mode vector, subscript T representing matrixes/vector transposition, u=[um(t) uf(t)
0]TExpression system input vector, G (q)=[(mcLj+md)gCφ-ρ -mcgCθ-ρ mcgLSθ-ρ]TExpression system gravity matrix, fd=
[fd1(t) fd2(t) fd3(t)]TIndicate that interference is vectorial, M (q),Indicate system inertia matrix and centripetal force-coriolis force
Matrix, expression are as follows:
Wherein,
It is as follows to define coordinate transformation relation:
Wherein, ξ1(t),ξ2(t),ξ3(t) system mode after representation transformation, ξ represent transformed state vector.It is based on
This, motive power model (1)-(4) can be converted to following form:
Wherein,The interference vector after arranging is represented,WithIt is after indicating conversion respectively
First derivatives and second dervative of the system state vector ξ about the time, are defined as follows:
Wherein,Represent system mode ξ after converting1(t),ξ2(t),ξ3(t) it is led about the single order of time
Number,Indicate system mode ξ after converting1(t),ξ2(t),ξ3(t) about the second dervative of time.Generation
Centripetal force-coriolis force matrix after table arrangement, concrete form are as follows:
Wherein,
Analysis can obtain, and transformed model has following property:
Property 1:Matrix M (q),Between meet following relationship,Wherein,Indicate first derivatives of the M (q) about the time.
Property 2:M (q) is positive definite matrix, and to arbitrary vectorThere is positive constant λm,λMMeet as follows
Relationship:
λm||x||2≤xTM(q)x≤λM||x||2 (10)
In real work, it is difficult to measure mc,mdExact value, its bound can generally be estimated, i.e.,
Wherein, m cIt indicates to load quality mcThe bound of estimation, m dIt indicates to mdThe bound of estimation.
On the other hand, lifting rope length when marine hoist is started to work should be in effective range, i.e.,
Lmin< L (0)=ξ2(0) < Lmax, (12)
Wherein, Lmin,LmaxThe minimum value and maximum value of effective lifting rope length are indicated respectively.It is similar with document [3]-[20],
It is assumed that earth coordinatesUnder load pivot angle | ξ3(t)|≤π/2。
It is an object of the present invention to design suitable control method, being accurately positioned and putting to marine hoist system load is realized
It is dynamic to inhibit control.In terms of the target mainly includes following three:1. in geodetic coordinatesUnder, it adjusts load situation and reaches its target
Position [ygd zgd], wherein ygd,zgdIt respectively representsThe y of load target position, z coordinate under coordinate system;2. inhibiting and eliminating
Geodetic coordinatesUnder hunting of load;3. during entire control, the lifting rope length of marine hoist system should be in effective range
It is interior, i.e.,
Lmin< L (t) < Lmax. (13)
It can be geodetic coordinatesThe coordinate representation of lower load situation is as follows:
According to above-mentioned control targe, ξ is needed3(t)=θ (t)-ρ (t) goes to zero, to inhibit earth coordinatesUnder it is negative
It carries and swings.At this point, the target location coordinate of load can be expressed as form:
ygd=Lj cos(ξ1),zgd=Lj sin(ξ1)-ξ2. (15)
Then, the control targe of system can indicate as follows:
yg→ygd,zg→zgd. (16)
Arrangement can obtain quantity of state ξ after coordinate transform1(t),ξ2(t),ξ3(t) target is as follows:
Wherein, arccos indicates inverse cosine function;So, the control targe of marine hoist system is converted into:Design is suitable
Control strategy so that ξ1(t),ξ2(t),ξ3(t) its target location is converged to respectively, i.e.,
ξ1→ξ1d,ξ2→ξ2d,ξ3→ξ3d=0. (18)
2nd, design of control law
For the control targe for realizing described in formula (18), it is as follows to define error signal:
e1=ξ1-ξ1d,e2=ξ2-ξ2d,e3=ξ3-ξ3d=ξ3 (19)
In formula, e1(t),e2(t),e3(t) quantity of state ξ is indicated respectively1(t),ξ2(t),ξ3(t) position error.It is peculiar to vessel to hang
The mechanical energy expression formula of vehicle system is as follows:
Wherein, E (t) indicates the mechanical energy of system.In next step, with ξ, ξ2(t),ξ3(t) q, L in E (t) are replaced respectively
(t), θ (t) can construct following function:
Formula (21) arranges as follows time derivation:
Assuming that systematic parameter is it is known that can directly design the control law of following form at this time:
Wherein,Indicate positive control gain.Using the control law, the control of system may be implemented
Target processed, while realizing to cantilever and loading the compensation of gravity.However, md,mcExact value be often difficult to obtain, therefore nothing
The control law (23) is applied in Practical Project by method.
To solve the above problems, The present invention gives a kind of control law considering parameter uncertainty, concrete form is such as
Under:
Wherein,For positive control gain, Lmax,LminIndicate the upper of effective rope length
Lower bound, γ1(e1),γ2(e2) indicate following auxiliary function:
γ1(e1)=α1s(e1),γ2(e2)=α2s(e2) (25)
Wherein,Positive parameter is represented, s (*) is a kind of saturation function, is defined as follows:
Wherein, the independent variable of * representative functions s (*).Analysis mode (25) and (26), it is known that following relationship is set up:
Theoretically, kp1,kd1,ki1,kp2,kd2,ki2,krMeet:
Wherein,It indicates to unknown mcAnd mdThe upper bound of estimation,m cIt indicates to load quality mcThe lower bound of estimation,Representative meets the normal number of relational expression (10),Indicate positive auxiliary parameter,Indicate auxiliary function γ3(ξ3) in parameter, γ3(ξ3) be defined as
Wherein, the definition of s (*) is referring to formula (26).
It is worth noting that being limited by the influence of Lyapunov analysis method conservative itself, provided in formula (28)
Only theoretically kp1,kd1,ki1,kp2,kd2,ki2,krNeed the condition met.It is sent out with after experiment test by largely emulating
It is existing, from the perspective of practical application, as long as choosing kp1,kd1,ki1,kp2,kd2,ki2,krFor just, control law (24) can be just
The control to marine hoist system is realized in often work.
3rd, stability analysis
This part will prove that control law proposed by the invention (24) can be in lasting ship by stringent mathematical analysis
In the case that body rolling disturbance and systematic parameter are unknown, make load running to it in earth coordinatesUnder target location,
And simultaneously effective inhibit hunting of load, i.e.,
Meanwhile in whole process, lifting rope length L (t) will be remained in effective range, i.e.,
Lmin< ξ2(t)=L (t) < Lmax. (31)
To prove the conclusion, some lemma are provided first.
Lemma 1:To arbitrarily meeting k > (mcLj+md) g positive real numberFollowing function f1(ξ1) it is positive definite integral form:
It proves:To f1(ξ1) about ξ1Derivation utilizes relationship e1=ξ1-ξ1d, obtain following result:
By formula (33) it is found that
Above formula shows ξ1=ξ1dIt is function f1(ξ1) a stationary point.Further, f1(ξ1) about ξ1Second dervative such as
Under:
By k > (mcLj+md) g is it is found that following relationship is set up:
In summary, ξ1=ξ1dIt is function f1(ξ1) minimum point.On the other hand, formula (34) and (36) are it is found that ξ1=ξ1d
For function f1(ξ1) unique stationary point.Therefore, ξ1=ξ1dIt is f1(ξ1) minimum point, f1(ξ1)≥f1(ξ1d)=0, i.e. function f1
(ξ1) it is positive definite integral form, formula (32) is set up.
Lemma 2:Work as ξ2=L > Lmin, and when meeting the constraints in formula (28), if minor function W (t) is non-negative:
Wherein, γ (e)=[γ1(e1) γ2(e2) γ3(ξ3)]T, γ3(ξ3) definition see formula (29).
It proves:By formula (10), (25)-(27), (29), the Section 2 in formula (37) can be organized into following form:
Work as ξ2=L > LminWhen, Section 3 arranges as follows in formula (37):
It can be obtained by formula (32),
To sum up, formula (37) can be rewritten as following form:
Therefore, when the constraints in formula (28) meets, W (t) is about e1(t),e2(t),e3(t) positive function, draws
Reason 2 is set up.
Lemma 3:WhenWhen, following inequality is set up:
|cos(ξ1)-cos(ξ1d)|≤kg|ξ1-ξ1d|=kg|e1|. (42)
It proves:It is of equal value with following inequality to be apparent from formula (42):
Ming Dynasty style (43) is set up as evidence, the auxiliary function being defined as follows:
f2(ξ1) to ξ1Derivation obtains
By formula (45) it is found thatThat is ξ1=ξ1dIt is f2(ξ1) stationary point.f2(ξ1) to ξ1Seek second order
It leads, and according toIt can obtain
Therefore, ξ1=ξ1dIt is f2(ξ1) maximum point.Meanwhile by formula (46), ξ can be obtained1=ξ1dIt is f2(ξ1) uniquely stay
Point, i.e. ξ1=ξ1dIt is f2(ξ1) maximum of points.So f2(ξ1)≥f2(ξ1d)=0 is set up, i.e. lemma 3 is set up.
It below will be to conclusion shown in formula (30), (31) into line justification.First, the scalar function being defined as follows:
Wherein,Indicate positive control gain, ψ1(t),ψw(t) it represents as follows
Auxiliary function:
Then, formula (47) is substituted into (24), and arranged, can be obtained to time derivation,
Formula (24) is substituted into formula (8), is arranged,
Wherein, mn2r=kr[(ξ2d-Lmax)/(ξ2-Lmax)3+(ξ2d-Lmin)/(ξ2-Lmin)3]e2+mcg[1-cos(ξ3)],
mn1r=(mcLj+md)g[cos(ξ1)-cos(ξ1d).Then, 6-7 in formula (49), it is rewritable as follows:
Formula (51) is substituted into formula (49), abbreviation can obtain
It is as follows that its upper bound can be obtained using Young inequality to the 7th on the right side of formula (52):
In next step, using lemma 3, the 8th in formula (52) can carry out following processing:
In above formula, property shown in formula (27) has been used.On the other hand, 9-10 in formula (52) can be handled as follows:
To the 11st in formula (52), using formula (9), result as follows can be obtained:
Then, to the 12nd in formula (52), relationship as follows can be obtained:
Further, using formula (26), (27), (29), relationship as follows can be obtained:
In next step, formula (53)-(58) are substituted into formula (52), arrange abbreviation and obtains,
According to the control gain constraint condition in formula (28), it is known that first 6 on the right side of formula (47) are non-positve term, and the 7th
Item still needs to further analyze.Since entire closed-loop system is continuous, it is known that the quantity of state of system can only consecutive variations, i.e. shape
Saltus step will not occur for the track of state amount.In view of lifting rope length L (t)=ξ2(t) initial value is in effective range, i.e. Lmin
< L (0)=ξ2(0) < Lmax[referring to formula (12)].Must then have moment T, when t ∈ [0, T) when, the coefficient before formula (59) the 7th
It is negative, i.e.-kr[(ξ2d-Lmax)/(ξ2-Lmax)3+(ξ2d-Lmin)/(ξ2-Lmin)3] < 0.Therefore, when t ∈ [0, T) when, by formula
(59) it can obtain,
Without loss of generality, it is assumed that ξ2(t) t ∈ [0, T) when, have disengaging section (Lmin,Lmax) trend.In view of ξ2(t)
It is the variable of consecutive variations, needs the boundary for reaching the section first, i.e., as t=T, ξ2(t)=LminOr ξ2(t)=Lmax;This
When, by the 7th in formula (47) it is found that V (t)=+ ∞.Simultaneously, it is contemplated that ξ2(t) continuity, then have
This and formula (60) conclusion contradiction.Therefore, it is known that ξ2(t) without departing from section (Lmin,Lmax), i.e.,
By formula (61) it is found that in formula (59) the 7th be it is negative, in summary,
Next, formula (47) is rewritten into following form:
By analyzing it is found that first 8 of formula (63) are non-negative.Then, lemma 1 and lemma 2 are utilized, it is known that remaining in formula (63)
Item is also positive definite.Therefore, function V (t) is positive definite integral form, can be used as Liapunov candidate functions.
Using formula (47) and (62), it can obtain and such as draw a conclusion:
Further, if e2(t) → 0, then have IfThen basisWith
It can obtainConvolution (64), it is known that
Due toIt is negative semidefinite, needs the asymptotic convergence using invariant set analytical proof closed-loop system.Definition is maximum constant
Collect Φ, is included in following set omega
According to formula (62), it is known that in set Φ
Formula (67) is substituted into formula (8), (24), is obtained
This also just illustrates that designed control law can accurately compensate cantilever and the gravity of load.
Finally, by formula (67) it is found that maximum invariant set utilizes Russell's principle of invariance only comprising closed-loop system equalization point
[11] provable formula (30) is set up.Meanwhile the result of formula (61) demonstrates rope length in whole process and is in effective range.By formula
(68) it can obtain, the control of system inputs um(t),uf(t) (m is finally converged to respectivelycLj+md)gcos(ξ1d),-mcG, it was demonstrated that this
Invention institute extracting method can handle md,mcUncertainty.
The advantages of the present invention:
For marine hoist (abbreviation ship is hung) system, the present invention proposes a kind of pendulum position control method that effectively disappears.Phase
Than existing method, this method is directed to the marine hoist system for being continued rolling interference by hull, considers parameter uncertainty, passes through
Suitable control strategy compensation gravity is designed, that realizes load is accurately positioned and swings inhibition, before having good practical application
Scape.
Description of the drawings:
Attached drawing 1 is the method for the present invention and control methods experimental result in 1 (embodiment 1) of experiment;ξ1(t),ξ2(t),ξ3
(t) system mode after representation transformation is specifically defined and sees formula (7);um(t),uf(t) indicate that cantilever torque and lifting rope are led respectively
Gravitation.
Specific implementation mode:
Embodiment 1:
1st, experimental procedure describes
1.1st, system control targe and corresponding constraint are determined
The control targe of marine hoist system includes following three part:1. in geodetic coordinatesUnder, adjust load situation
Reach its target location [ygd zgd], wherein ygd,zgdIt respectively representsThe coordinate of load target position under coordinate system;2. inhibiting
With elimination geodetic coordinatesUnder hunting of load;3. during entire control, the lifting rope length of marine hoist system, which should be in, to be had
It imitates in range, i.e.,
Lmin< L (t) < Lmax (13)
Wherein, L (t) indicates the lifting rope length of marine hoist system, the t expression times in bracket, and (t) is indicated behind variable
The variable is the function about the time, Lmin,LmaxThe lower limit and the upper limit of effective lifting rope length are indicated respectively.
1.2nd, error signal and auxiliary function are defined
Introduce following coordinate transform:
Wherein, subscript T representing matrixes/vector transposition, φ (t) indicate that the pitch angle of cantilever, L (t) indicate the length of lifting rope,
θ (t) indicates that load pivot angle, ρ (t) indicate that hull roll angle caused by wave, ξ represent transformed state vector, ξ1(t),ξ2
(t),ξ3(t) system state amount after representation transformation, the t in bracket indicate the time, behind variable (t) indicate the variable be about
It is subsequent (t) to omit most number variable for simplicity for the function of time;Using above-mentioned coordinate transformation method, in conjunction with system
Control targe, the target location of quantity of state is as follows after can must converting:
Wherein, arccos indicates inverse cosine function, ygd,zgdRepresent the target location coordinate of load, LjRepresent the length of cantilever
Degree, ξ1d,ξ2d,ξ3dRespectively represent quantity of state ξ after converting1(t),ξ2(t),ξ3(t) target location.
Further, error signal e is defined1(t),e2(t),e3(t) as follows:
e1=ξ1-ξ1d,e2=ξ2-ξ2d,e3=ξ3-ξ3d=ξ3 (19)
Then error signal is about the derivative of time:
Wherein,Respectively represent ξ1(t),ξ2(t),ξ3(t) about the derivative of time.Define auxiliary function
γ1(e1),γ2(e2),γ3(ξ3) as follows:
Wherein,Indicate positive parameter;Function s (*'s) is defined as follows:
Wherein, the independent variable of * representative functions s (*).
1.3rd, control law determines
Design cantilever pitch moment um(t) and lifting rope tractive force uf(t) control law is as follows:
Wherein,For positive control gain.
1.4th, control method is realized
Using the sensor on marine hoist, the pitch angle φ (t) and angular speed of cantilever are measuredThe length L of lifting rope
(t) and long change of rope speedHull roll angle ρ (t) and its angular speedUsing formula (24), control is calculated in real time
Signal, for controlling corresponding driving motor, realization accurately controls marine hoist system.
2nd, experimental result describes
To verify the validity of institute's extracting method of the present invention, according to above-mentioned steps, carried out on marine hoist experiment porch real
It tests.Cantilever rotary inertia, jib-length in experiment porch etc. are as follows:
J=0.2457kgm2,Lj=0.65m, md=0.29kgm, g=9.8m/s2
The initial value of system mode is selected as ξ1(0)=0rad, ξ2(0)=0.6m, ξ3(0)=0rad;Wherein, rad is indicated
Radian, m indicate rice.The target location coordinate being supported under earth coordinates iszgd=0.125m is utilized
Corresponding system mode target can be calculated in formula (17)
ξ1d=π/6rad (30deg), ξ2d=0.2m, ξ3d=0rad
Wherein, deg degree of a representations.The rolling disturbance of hull is set as
The Significant Change range of rope length is set as (Lmin,Lmax)=(0.18,1.0) [m].Assuming that mdIt is unknown, and above and below it
Boundary is estimated as m d=0.2kgm.
2.1st, 1 is tested:It is compared with existing method.This experiment will be verified being accurately positioned in load of institute extracting method, be swung
Validity in terms of inhibition, and itself and the method in document [16] are compared.This tests the essence of selected load quality
Really value is mc=0.34kg assumes that it is unknown in experiment, estimates of upper and lower bounds is m c=0.2kg.By multiple
It tests, the control gain in document [16] in control methods is selected as:
k1=25.5, k2=9.6, k3=3.3, kα=0.12, kβ=0.23, kL1=20.7, kL2=6.3, kx=1.1, σ
=0.015,
And the control gain of the method for the present invention is selected as:
kp1=18, kd1=9.9, ki1=2, kp2=27, kd2=4.1, ki2=0.4, α1=0.1, α2=0.02, kr=
0.01。
Attached drawing 1 gives experimental result, wherein the system after coordinate transform is set forth in 5 subgraphs from top to bottom
Quantity of state ξ1(t),ξ2(t),ξ3(t) and system control inputs um(t),uf(t) curve changed over time;Solid line in attached drawing 1
The method of the present invention and the experimental result of control methods are respectively represented with dotted line;1st subgraph and the 2nd (from top to bottom) in attached drawing 1
Dotted line in a subgraph indicates ξ respectively1(t),ξ2(t) target location ξ1d,ξ2d.Meanwhile experimental result is shown for convenience,
ξ1(t),ξ3(t) unit of curve has been converted into angle (deg) from radian (rad).
As can be seen that two methods can be with driving condition amount ξ from attached drawing 11(t),ξ2(t),ξ3(t) it reaches corresponding
Target, i.e. driving load reach its target location.But the experimental result of control methods is there are apparent overshoot, and regulating time compared with
It is long;And the experimental result of the method for the present invention there's almost no overshoot.On the other hand, although can be seen that from curve shown in dotted line
Control methods may be implemented the inhibition to hunting of load, but when loading the Residual oscillations after reaching target and continue for long
Between;And in the range of hunting of load can be restricted to smaller by the experimental result (shown in solid) of the method for the present invention, while almost
There is no Residual oscillations.From last two subgraphs it can also be seen that the control input curve of the method for the present invention is compared with control methods
It is more smooth, it is easier to engineer application.
Bibliography
[1]X.Zhang,B.Xian,B.Zhao,and Y.Zhang,“Autonomous flight control ofa
nano quadrotor helicopter in a GPS-denied environment using on-board vision,”
IEEE Transactions on IndustrialElectronics,vol.62,no.10,pp.6392-6403,2015.
[2]Z.Li,H.Liu,B.Zhu,H.Gao,and O.Kaynak,“Nonlinear robust attitude
tracking control of a table-mount experimental helicopter using output
feedback,”IEEE Transactions on IndustrialElectronics,vol.62,no.9,pp.5665-
5676,2015.
[3]S.Garrido,M.Abderrahim,A.Giménez,R.Diez,and C.Balaguer,“Anti-
swinging input shaping control of an automatic construction crane,”IEEE
Transactions on Automation Science andEngineering,vol.5,no.3,pp.549-557,2008.
[4]K.L.Sorensen,W.Singhose,and S.Dickerson,“A controller enabling
precise positioning and sway reduction in bridge and gantry cranes,”
ControlEngineering Practice,vol.15,no.7,pp.825-837,2007.
[5]J.Huang,X.Xie,and Z.Liang,“Control ofbridge cranes with
distributed mass payload dynamics,”IEEE/ASME Transactions on Mechatronics,
vol.20,no.1,pp.481-486,2015.
[6]N.Sun,Y.Fang,Y.Zhang,and B.Ma,“A novel kinematic coupling-based
trajectory planning method for overhead cranes,”IEEE/ASME Transactions on
Mechatronics,vol.17,no.1,pp.166-173,2012.
[7]Z.Wu and X.Xia,“Optimal motion planning for overhead cranes,”IET
Control Theory&Applications,vol.8,no.17,pp.1833–1842,2014.
[8]N.Uchiyama,H.Ouyang,and S.Sano,“Simple rotary crane dynamics
modeling and open-loop control for residual load sway suppression by only
horizontal boom motion,”Mechatronics,vol.23,no.8,pp.1223-1236,2013.
[9]W.He,S.Zhang,and S.S.Ge,“Adaptive control ofa flexible crane
system with the boundary output constraint,”IEEE Transactions on
IndustrialElectronics,vol.61,no.8,pp.4126-4133,2014.
[10]R.Liu,S.Li,and S.Ding,“Nested saturation control for overhead
crane systems,”Transactions oftheInstitute ofMeasurement and Control,vol.34,
no.7,pp.862-875,2012.
[11]N.Sun,Y.Fang,H.Chen,B.Lu,and Y.Fu,“Slew/translation positioning
and swing suppression for 4-DOF tower cranes with parametric uncertainties:
Design and hardware experimentation,”IEEE Transactions on
IndustrialElectronics,vol.63,no.10,pp.6407-6418,2016.
[12]X.Wu and X.He,“Enhanced damping-based anti-swing control method
for underactuated overhead cranes,”IET Control Theory&Applications,vol.9,
no.12,pp.1893–1900,2015.
[13]A.Rauh,L.Senkel,J.Gebhardt,and H.Aschemann,“Stochastic methods
for the control of crane systems in marine applications,”in Proceedings ofthe
European Control Conference,Strasbourg,France,June 2014,pp.2998-3003.
[14]B.Kimiaghalam,A.Homaifar,M.Bikdash,and B.R.Hunt,“Feedforward
control law for a shipboard crane with Maryland rigging system,”Journal of
Vibration and Control,vol.8,no.2,pp.159-188,2002.
[15]Y.Qian and Y.Fang,“A learning strategy based partial feedback
linearization control method for an offshore boom crane,”in Proceedings of
the IEEE Conference on Decision and Control,Osaka,Japan,Dec.2015,pp.6737-
6742.
[16]Y.Fang,P.Wang,N.Sun,and Y.Zhang,“Dynamics analysis and nonlinear
control ofan offshore boom crane,”IEEE Transactions on Industrial
Electronics,vol.61,no.1,pp.414-427,2014.
[17]Q.H.Ngo and K.-S.Hong,“Sliding-mode antisway control of an
offshore container crane,”IEEE/ASME Transactions on Mechatronics,vol.17,no.2,
pp.201-209,2012.
[18]R.M.T.Raja Ismail and Q.P.Ha,“Trajectory tracking and anti-sway
control of three-dimensional offshore boom cranes using second-order sliding
modes,”in Proceedings of the IEEE International Conference on Automation
Science and Engineering,Madison,USA,Aug.2013,pp.996-1001.
[19]H.-S.Park and N.-T.Le,“Modeling and controlling the mobile
harbour crane system with virtual prototyping technology,”International
Journal of Control,Automation,andSystems,vol.10,no.6,pp.1204-1214,2012.
[20]B.Kimiaghalam,A.Homaifar,and M.Bikdash,“Pendulation suppression
of a shipboard crane using fuzzy controller,”in Proceedings ofthe American
Control Conference,San Diego,USA,June 1999,pp.586-590。
Claims (1)
1. a kind of marine hoist control method of consideration lasting interference and parameter uncertainty, it is characterised in that this method includes:
1st, system control targe and corresponding constraint are determined
The control targe of marine hoist system includes following three part:1. in geodetic coordinatesUnder, it adjusts load situation and reaches
Its target location [ygd zgd], wherein ygd,zgdIt respectively representsThe coordinate of load target position under coordinate system;2. inhibiting and disappearing
Except geodetic coordinatesUnder hunting of load;3. during entire control, the lifting rope length of marine hoist system should be in effective model
In enclosing, i.e.,
Lmin< L (t) < Lmax (13)
Wherein, L (t) indicates the lifting rope length of marine hoist system;T in bracket indicates the time, and (t) indicates the change behind variable
It is subsequent (t) to omit most number variable for simplicity for the function about the time for amount;Lmin,LmaxEffective lifting rope is indicated respectively
The lower limit and the upper limit of length;
2nd, error signal and auxiliary function are defined
Introduce following coordinate transform:
Wherein, subscript T representing matrixes/vector transposition, φ (t) indicate that the pitch angle of cantilever, L (t) indicate the length of lifting rope, θ (t)
Indicate that load pivot angle, ρ (t) indicate that hull roll angle caused by wave, ξ represent transformed state vector, ξ1(t),ξ2(t),ξ3
(t) system state amount after representation transformation, the t in bracket indicate the time, and (t) indicates that the variable is about the time behind variable
It is subsequent (t) to omit most number variable for simplicity for function;Using above-mentioned coordinate transformation method, in conjunction with the control mesh of system
Mark, the target location of quantity of state is as follows after can must converting:
Wherein, arccos indicates inverse cosine function, ygd,zgdRepresent the target location coordinate of load, LjThe length of cantilever is represented,
ξ1d,ξ2d,ξ3dRespectively represent quantity of state ξ after converting1(t),ξ2(t),ξ3(t) target location;
Further, error signal e is defined1(t),e2(t),e3(t) as follows:
e1=ξ1-ξ1d,e2=ξ2-ξ2d,e3=ξ3-ξ3d=ξ3 (19)
Then error signal is about the derivative of time:
Wherein,Respectively represent ξ1(t),ξ2(t),ξ3(t) about the derivative of time;It is defined as follows auxiliary function
γ1(e1),γ2(e2),γ3(ξ3):
Wherein, α1,α2,Indicate positive parameter, function s (*'s) is defined as follows:
Wherein, the independent variable of * representative functions s (*);
3rd, control law determines
Design cantilever pitch moment um(t) and lifting rope tractive force uf(t) control law is as follows:
Wherein, kp1,kd1,ki1,kp2,kd2,ki2,For positive control gain;
4th, control method is realized
Using the sensor on marine hoist, the pitch angle φ (t) and angular speed of cantilever are measuredThe length L (t) of lifting rope and
Long change of rope speedHull roll angle ρ (t) and its angular speedUsing formula (24), control signal is calculated in real time,
For controlling corresponding driving motor, realization accurately controls marine hoist system.
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