CN114597918A - Method and system for determining inertia control delay meeting frequency stability constraint - Google Patents

Method and system for determining inertia control delay meeting frequency stability constraint Download PDF

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CN114597918A
CN114597918A CN202210420928.XA CN202210420928A CN114597918A CN 114597918 A CN114597918 A CN 114597918A CN 202210420928 A CN202210420928 A CN 202210420928A CN 114597918 A CN114597918 A CN 114597918A
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inertia control
delay
inertia
frequency
coefficient
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CN114597918B (en
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孙华东
王宝财
李文锋
魏巍
张健
杨超
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China Electric Power Research Institute Co Ltd CEPRI
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    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02J—CIRCUIT ARRANGEMENTS OR SYSTEMS FOR SUPPLYING OR DISTRIBUTING ELECTRIC POWER; SYSTEMS FOR STORING ELECTRIC ENERGY
    • H02J3/00—Circuit arrangements for ac mains or ac distribution networks
    • H02J3/24—Arrangements for preventing or reducing oscillations of power in networks
    • H02J3/241—The oscillation concerning frequency
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02J—CIRCUIT ARRANGEMENTS OR SYSTEMS FOR SUPPLYING OR DISTRIBUTING ELECTRIC POWER; SYSTEMS FOR STORING ELECTRIC ENERGY
    • H02J3/00—Circuit arrangements for ac mains or ac distribution networks
    • H02J3/38—Arrangements for parallely feeding a single network by two or more generators, converters or transformers
    • H02J3/46—Controlling of the sharing of output between the generators, converters, or transformers
    • H02J3/466—Scheduling the operation of the generators, e.g. connecting or disconnecting generators to meet a given demand
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02J—CIRCUIT ARRANGEMENTS OR SYSTEMS FOR SUPPLYING OR DISTRIBUTING ELECTRIC POWER; SYSTEMS FOR STORING ELECTRIC ENERGY
    • H02J2203/00—Indexing scheme relating to details of circuit arrangements for AC mains or AC distribution networks
    • H02J2203/20—Simulating, e g planning, reliability check, modelling or computer assisted design [CAD]
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/76—Power conversion electric or electronic aspects

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Abstract

The invention discloses a method and a system for determining inertia control delay meeting frequency stability constraint, which comprises the following steps: establishing a system frequency response model containing new energy inertia control and droop control, and determining model parameters of the system frequency response model; calculating a first inertia control coefficient which is not influenced by time delay based on the model parameters; setting an inertia control coefficient based on the first inertia control coefficient and the model parameter, and determining the inertia control maximum delay which is stably constrained by small disturbance and the inertia control optimal delay which is stably constrained by large disturbance frequency corresponding to the set inertia control coefficient; and determining the inertia control delay meeting the frequency stability constraint according to the inertia control maximum delay and the inertia control optimal delay. According to the invention, the inertia control delay time meeting the frequency stability constraint is calculated, so that the frequency oscillation can be inhibited while the frequency maximum deviation is improved to the maximum extent.

Description

Method and system for determining inertia control delay meeting frequency stability constraint
Technical Field
The present invention relates to the field of power system control technologies, and more particularly, to a method and system for determining an inertia control delay that satisfies a frequency stability constraint.
Background
The access of a large-scale power electronic power supply with almost no frequency response to a power grid causes the frequency response capability of a system to be sharply reduced, and the system frequency stability only depending on the inertia response and frequency adjustment of a conventional unit faces challenges. And links such as frequency control are added to the new energy, so that the inertia level of the system can be improved, and the frequency index under disturbance can be improved.
The new energy additional inertia control can be divided into two types, namely voltage source type control based on a Virtual Synchronous Generator (VSG) and current source type control based on feedback system frequency according to different power source properties. The voltage source type inertia control can realize the inertia response external characteristic which is the same as that of a synchronous machine, but the design is complex, and the practical engineering application is less; while the current source type inertia control of the feedback system frequency is simple to implement, there is a short delay caused by measurement and communication. In terms of energy sources, the energy can be from static energy storage or the rotating kinetic energy of a fan shafting. For current source type frequency control, although the frequency index under large disturbance is improved by setting a control parameter only considering the stability of the frequency of large disturbance, the frequency stability of small disturbance of the system may be deteriorated, and frequency oscillation may be caused.
At present, the power electronic power supply inertia control is mainly researched from improving one of a large disturbance frequency index and a small disturbance stability analysis, two factors are considered in the research, the problem of frequency oscillation possibly caused by measurement and communication delay for current source type frequency control is solved, and a control parameter stability range calculation method constrained by small disturbance frequency stability is lacked in the research. In the aspect of large disturbance frequency stability, only the improvement of new energy inertia control on the frequency change rate of the system is considered, the influence of inertia control on the maximum frequency deviation is not considered, and in the current system which focuses more on the maximum frequency deviation, the flexibility of power electronic control is fully utilized to improve different frequency indexes.
Therefore, how to design and consider the current source type inertia control parameters with stable small disturbance and large disturbance frequency is a problem to be solved urgently at present.
Disclosure of Invention
The invention provides a method and a system for determining inertia control delay meeting frequency stability constraint, and aims to solve the problem of how to determine new energy inertia control parameters.
In order to solve the above problem, according to an aspect of the present invention, there is provided a method of determining an inertia control delay satisfying a frequency stability constraint, the method including:
establishing a system frequency response model containing new energy inertia control and droop control, and determining model parameters of the system frequency response model;
calculating a first inertia control coefficient which is not influenced by time delay based on the model parameters;
setting an inertia control coefficient based on the first inertia control coefficient and the model parameter, and determining the inertia control maximum delay which is stably constrained by small disturbance and the inertia control optimal delay which is stably constrained by large disturbance frequency corresponding to the set inertia control coefficient;
and determining the inertia control delay meeting the frequency stability constraint according to the inertia control maximum delay and the inertia control optimal delay.
Preferably, the model parameters include: primary frequency modulation droop coefficient K of generatorGInertia constant H, load frequency regulation coefficient D, response time T, damping ratio
Figure 112593DEST_PATH_IMAGE001
And natural frequency
Figure 43640DEST_PATH_IMAGE002
(ii) a Wherein the content of the first and second substances,
Figure 63549DEST_PATH_IMAGE003
KG=1/R，
wherein R is a difference adjustment coefficient.
Preferably, wherein calculating a first maximum inertia control coefficient not affected by a delay according to the magnitude conditional expression includes:
Figure 472665DEST_PATH_IMAGE004
wherein, the first and the second end of the pipe are connected with each other,
Figure 792787DEST_PATH_IMAGE005
a first maximum inertia control coefficient; h is an inertia constant, and T is response time;
Figure 363577DEST_PATH_IMAGE001
is the damping ratio;
Figure 277307DEST_PATH_IMAGE002
is the natural frequency; d is the load frequency regulation factor, KGIs the primary frequency modulation droop coefficient of the generator, H is the inertia constant, T is the response time,
Figure 614747DEST_PATH_IMAGE006
。
preferably, the determining of the inertia control maximum delay constrained by small disturbance stability and the inertia control optimal delay constrained by large disturbance frequency stability corresponding to the set inertia control coefficient includes:
Figure 399163DEST_PATH_IMAGE007
wherein the content of the first and second substances,
Figure 531067DEST_PATH_IMAGE008
controlling the maximum delay for the inertia corresponding to the set inertia control coefficient;
Figure 400935DEST_PATH_IMAGE009
controlling the coefficient for the set inertia;
Figure 417432DEST_PATH_IMAGE010
controlling optimal delay for inertia corresponding to the set inertia control coefficient;
Figure 446568DEST_PATH_IMAGE011
and
Figure 359160DEST_PATH_IMAGE012
the first cut-off frequency and the second cut-off frequency are respectively corresponding to the set inertia control coefficients;
Figure 372116DEST_PATH_IMAGE001
is the damping ratio;
Figure 661146DEST_PATH_IMAGE002
is a natural frequency; d is a load frequency adjusting coefficient; kGThe droop coefficient is the primary frequency modulation of the generator; h is an inertia constant; t is response time;
Figure 685733DEST_PATH_IMAGE013
the inverse of the response time T.
Preferably, the determining an inertia control delay satisfying a frequency stability constraint according to the inertia control maximum delay and the inertia control optimal delay includes:
if the inertia control optimal delay is smaller than the inertia control maximum delay, determining inertia control delay meeting frequency stability constraint according to the inertia control optimal delay;
otherwise, determining the inertia control delay meeting the frequency stability constraint according to the inertia control maximum delay.
According to another aspect of the present invention, there is provided a system for determining an inertia control delay that satisfies a frequency stability constraint, the system comprising:
the model establishing unit is used for establishing a system frequency response model containing new energy inertia control and droop control and determining model parameters of the system frequency response model;
the first inertia control coefficient determining unit is used for calculating a first inertia control coefficient which is not influenced by time delay based on the model parameters;
the maximum delay and optimal delay calculation unit is used for setting an inertia control coefficient based on the first inertia control coefficient and the model parameter, and determining the inertia control maximum delay which is stably constrained by small disturbance and the inertia control optimal delay which is stably constrained by large disturbance frequency corresponding to the set inertia control coefficient;
and the delay determining unit is used for determining the inertia control delay meeting the frequency stability constraint according to the inertia control maximum delay and the inertia control optimal delay.
Preferably, in the model establishing unit, the model parameters include: primary frequency modulation droop coefficient K of generatorGInertia constant H, load frequency regulation coefficient D, response time T, damping ratio
Figure 159440DEST_PATH_IMAGE001
And natural frequency
Figure 3899DEST_PATH_IMAGE002
(ii) a Wherein the content of the first and second substances,
Figure 627779DEST_PATH_IMAGE003
KG=1/R，
wherein R is a difference adjustment coefficient.
Preferably, the calculating a first maximum inertia control coefficient that is not affected by a delay according to the magnitude conditional expression by the first maximum inertia control coefficient determining unit includes:
Figure 506873DEST_PATH_IMAGE004
wherein the content of the first and second substances,
Figure 885902DEST_PATH_IMAGE005
a first maximum inertia control coefficient; h is an inertia constant, and T is response time;
Figure 483236DEST_PATH_IMAGE001
is the damping ratio;
Figure 238703DEST_PATH_IMAGE002
is a natural frequency; d is the load frequency regulation factor, KGIs the primary frequency modulation droop coefficient of the generator, H is the inertia constant, T is the response time,
Figure 255461DEST_PATH_IMAGE006
。
preferably, the determining, by the maximum delay and optimal delay calculating unit, the inertia control maximum delay constrained by small disturbance stability and the inertia control optimal delay constrained by large disturbance frequency stability, which correspond to the set inertia control coefficient, includes:
Figure 211916DEST_PATH_IMAGE014
wherein the content of the first and second substances,
Figure 890022DEST_PATH_IMAGE008
controlling the maximum delay for the inertia corresponding to the set inertia control coefficient;
Figure 590124DEST_PATH_IMAGE009
controlling the coefficient for the set inertia;
Figure 302865DEST_PATH_IMAGE010
controlling optimal delay for inertia corresponding to the set inertia control coefficient;
Figure 430221DEST_PATH_IMAGE011
and
Figure 736569DEST_PATH_IMAGE012
the first cut-off frequency and the second cut-off frequency are respectively corresponding to the set inertia control coefficient;
Figure 833838DEST_PATH_IMAGE001
is the damping ratio;
Figure 542031DEST_PATH_IMAGE002
is a natural frequency; d is a load frequency adjusting coefficient; kGThe droop coefficient is the primary frequency modulation of the generator; h is an inertia constant; t is response time;
Figure 840288DEST_PATH_IMAGE013
the inverse of the response time T.
Preferably, the determining, by the delay determining unit, an inertia control delay satisfying a frequency stability constraint according to the inertia control maximum delay and the inertia control optimal delay includes:
if the inertia control optimal delay is smaller than the inertia control maximum delay, determining inertia control delay meeting frequency stability constraint according to the inertia control optimal delay;
otherwise, determining the inertia control delay meeting the frequency stability constraint according to the inertia control maximum delay.
Based on a further aspect of the invention, a computer-readable storage medium is provided, having stored thereon a computer program which, when being executed by a processor, carries out the steps of any of the methods of determining an inertia control delay time that satisfies a frequency stability constraint.
Based on another aspect of the present invention, the present invention provides an electronic device comprising:
the computer-readable storage medium described above; and
one or more processors to execute the program in the computer-readable storage medium.
The invention provides a method and a system for determining inertia control delay meeting frequency stability constraint, which comprises the following steps: establishing a system frequency response model containing new energy inertia control and droop control, and determining model parameters of the system frequency response model; calculating a first inertia control coefficient which is not influenced by time delay based on the model parameters; setting an inertia control coefficient based on the first inertia control coefficient and the model parameter, and determining the inertia control maximum delay which is stably constrained by small disturbance and the inertia control optimal delay which is stably constrained by large disturbance frequency corresponding to the set inertia control coefficient; and determining the inertia control delay meeting the frequency stability constraint according to the inertia control maximum delay and the inertia control optimal delay. The setting of the inertia control coefficient is carried out based on the selection range of the inertia control coefficient, so that the frequency oscillation can be inhibited; based on the set inertia control coefficient, the inertia control maximum delay constrained by small disturbance stability and the inertia control optimal delay constrained by large disturbance frequency stability are determined, and the inertia control delay meeting the frequency stability constraint is calculated based on the inertia control maximum delay and the inertia control optimal delay, so that the frequency maximum deviation can be improved to the maximum extent.
Drawings
Exemplary embodiments of the invention may be more completely understood in consideration of the following drawings:
FIG. 1 is a flow diagram of a method 100 of determining an inertia control delay that satisfies a frequency stability constraint according to an embodiment of the invention;
FIG. 2 is a schematic diagram of a system frequency response model according to an embodiment of the invention;
FIG. 3 is a schematic diagram of a simplified system frequency response model according to an embodiment of the present invention;
FIGS. 4 (a) and (b) are schematic diagrams of amplitude-phase curves and frequency curves, respectively, of inertia control on stability according to an embodiment of the present invention;
fig. 5 (a) and (b) are diagrams illustrating amplitude-phase curves and frequency curves, respectively, of the effect of time delay on stability when inertia control coefficients are small according to an embodiment of the present invention;
fig. 6 (a) and (b) are schematic diagrams of amplitude-phase curves and frequency curves, respectively, of the effect of time delay on stability when the inertia control coefficient is large according to an embodiment of the present invention;
FIG. 7 is a schematic diagram of a dominant pole change trajectory according to an embodiment of the present invention;
FIG. 8 is a schematic illustration of frequency versus inertia support power according to an embodiment of the invention;
FIG. 9 is a diagram illustrating a phase angle margin versus delay according to an embodiment of the present invention;
FIG. 10 is a schematic diagram of a WSCC 9 bus bar system according to an embodiment of the present invention;
FIG. 11 is a schematic diagram of frequency curves for different inertia control parameters according to an embodiment of the present invention;
FIG. 12 is a diagram illustrating the effect of delay on frequency according to an embodiment of the present invention;
fig. 13 is a block diagram of a system 1300 for determining an inertia control delay that satisfies a frequency stability constraint according to an embodiment of the invention.
Detailed Description
The exemplary embodiments of the present invention will now be described with reference to the accompanying drawings, however, the present invention may be embodied in many different forms and is not limited to the embodiments described herein, which are provided for complete and complete disclosure of the present invention and to fully convey the scope of the present invention to those skilled in the art. The terminology used in the exemplary embodiments illustrated in the accompanying drawings is not intended to be limiting of the invention. In the drawings, the same units/elements are denoted by the same reference numerals.
Unless otherwise defined, terms (including technical and scientific terms) used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. Further, it will be understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the relevant art and will not be interpreted in an idealized or overly formal sense.
FIG. 1 is a flow diagram of a method 100 of determining an inertia control delay that satisfies a frequency stability constraint according to an embodiment of the invention. As shown in fig. 1, the method for determining an inertia control delay time satisfying a frequency stability constraint according to the embodiment of the present invention can suppress the occurrence of frequency oscillation while improving the maximum frequency deviation to the maximum extent by calculating the inertia control delay time satisfying the frequency stability constraint. The method 100 for determining the inertia control delay meeting the frequency stability constraint provided by the embodiment of the invention starts from step 101, establishes a system frequency response model containing new energy inertia control and droop control in step 101, and determines model parameters of the system frequency response model.
Preferably, wherein in the system frequency response model, the disturbance power Δ PdGenerating a frequency deviation delta f after the system frequency response; the new energy inertia control provides inertia support power delta P for the system according to the function of the frequency change rate of the systemin(ii) a The new energy droop control provides primary frequency modulation power delta P to the system according to the frequency deviation function of the systemdr(ii) a After the new energy inertia support and the droop control act together, the unbalanced power of the system is reduced.
Preferably, the model parameters include: primary frequency modulation droop coefficient K of generatorGInertia constant H, load frequency regulation coefficient D, response time T, damping ratio
Figure 492987DEST_PATH_IMAGE001
And natural frequency
Figure 269313DEST_PATH_IMAGE002
(ii) a Wherein the content of the first and second substances,
Figure 363171DEST_PATH_IMAGE003
KG=1/R，
wherein R is a difference adjustment coefficient.
In the embodiment of the invention, a system frequency response model containing new energy inertia control and droop control is established. Wherein the system frequency characteristics are generally described as a single-machine-band concentrated load model, as shown in FIG. 2, the conventional unit primary frequency modulation is represented as a thermal power unit without a reheater, where TCHIs the time constant of the steam chamber, TGAs time constant of the governor, KGIs the primary frequency modulation droop coefficient of the generator, KGAnd R is a difference adjustment coefficient. Hin(s) and HdrAnd(s) are respectively a new energy inertia control transfer function and a droop control transfer function. The equivalent rotor equation of motion is:
Figure 691384DEST_PATH_IMAGE015
，
in the formula, H is the inertia constant, D is the load frequency adjustment coefficient, Δ f is the inertia center frequency, Δ Pm、∆PinAnd Δ PdrRespectively controlling the primary frequency modulation power, the new energy inertia control support power and the new energy droop control power variable quantity, PdIs the perturbation power.
In order to study the influence of the new energy frequency control on the system stability, the primary frequency modulation of the conventional unit is equivalent to first-order inertia (1/(1 + Ts), T is response time), and the primary frequency modulation is combined with a feedforward link and is equivalent to G(s), so that fig. 2 can be further simplified into fig. 3. Wherein the disturbance power DeltaPdGenerating a frequency deviation delta f after system frequency response; the new energy inertia control provides inertia support power delta P for the system according to the frequency change rate action of the systemin(ii) a The new energy droop control provides primary frequency modulation power delta P to the system according to the frequency deviation function of the systemdr(ii) a And after the new energy inertia support and the droop control act together, the unbalanced power of the system is reduced.
Wherein G(s) is a conventional unit inertia and primary frequency modulation transfer function, and comprises:
Figure 972323DEST_PATH_IMAGE016
，
Figure 411395DEST_PATH_IMAGE017
，
Figure 828601DEST_PATH_IMAGE018
；
the current source type inertia quantity with time delay is controlled as follows:
Figure 468661DEST_PATH_IMAGE019
，
the system open loop transfer function is then:
Figure 95951DEST_PATH_IMAGE020
，
the amplitude condition is as follows:
Figure 214080DEST_PATH_IMAGE021
，
the amplitude margin is then:
Figure 282530DEST_PATH_IMAGE022
，
the phase angle conditions are:
Figure 218125DEST_PATH_IMAGE023
，
the phase angle margin is then:
Figure 942499DEST_PATH_IMAGE024
，
in the formula, ωcIs the cut-off frequency, H is the inertia constant, T is the response time;
Figure 988952DEST_PATH_IMAGE025
is the damping ratio; omeganIs a natural frequency; d is the load frequency regulation factor, KGThe droop coefficient of the primary frequency modulation of the generator is H, the inertia constant is H, and T is response time.
At step 102, a first inertia control coefficient, which is not affected by the delay, is calculated based on the model parameters.
Preferably, wherein calculating a first maximum inertia control coefficient not affected by a delay according to the magnitude conditional expression includes:
Figure 646330DEST_PATH_IMAGE004
wherein the content of the first and second substances,
Figure 622333DEST_PATH_IMAGE005
a first maximum inertia control coefficient; h is an inertia constant, and T is response time;
Figure 958636DEST_PATH_IMAGE001
is the damping ratio;
Figure 684147DEST_PATH_IMAGE002
is a natural frequency; d is the load frequency regulation factor, KGIs the primary frequency modulation droop coefficient of the generator, H is the inertia constant, T is the response time,
Figure 930451DEST_PATH_IMAGE006
。
according to the automatic control theory, the inertia control coefficient only changes the amplitude characteristic to change the amplitude margin, and the time delay only changes the phase-frequency characteristic to change the phase angle margin. And calculating the inertia control coefficient and the delay range under the stable constraint of the small disturbance frequency according to the amplitude margin and the phase angle margin.
As can be seen from the formula amplitude condition formula, as the frequency increases, the amplitude margin L (ω) = KinH, stabilization of condition L (ω) according to amplitude margin<1, can be obtained as Kin>H, system instability. FIG. 4 (a) shows different inertia control coefficients KinLower amplitude-phase curve (delay τ)in=0.1 s), it can be seen that with KinThe phase-frequency characteristic is not changed, the amplitude-frequency characteristic is gradually moved upwards, the amplitude margin is gradually reduced, the stability is deteriorated, and the corresponding frequency curve is shown in (b) of fig. 4 when K is reachedinAnd when the frequency is not less than 1.1H, the system is unstable in oscillation.
When K isin<H, the system small disturbance stability depends on KinAnd a delay of tauinSpecific numerical values. At KinIn the smaller case (K)in= H/3), where the amplitude-frequency characteristic does not intersect the 0dB line, the corresponding phase angle margin is infinite, that is, the delay does not cause system frequency oscillation, as shown in (a) of fig. 5, and the frequency curve corresponding to the delay is shown in (b) of fig. 5, it can be seen that the frequencies under different delays are frequency curvesThe rate curves were all stable.
Coefficient of inertia control KinWhen the amplitude-frequency curve is shifted upward and intersects with the 0dB line, there is a phase angle margin, that is, there is a delay value range for stabilizing the system, as shown in fig. 6, where fig. 6 (a) is the amplitude-frequency curve and the phase-frequency curve at different delays, and fig. 6 (b) is the frequency curve at different delays. It can be seen that as the time delay increases, the frequency stability of the small disturbance of the system becomes worse when tau is increasedinAnd =0.8s, the system frequency oscillation is unstable.
According to the analysis, the selection range of the inertia control parameters can be limited by the stability of the small disturbance frequency.
In the embodiment of the invention, the value range of the inertia control coefficient which is not influenced by time delay is calculated based on the amplitude condition. Let L (ω) =1, the amplitude condition may be collated as:
Figure 942270DEST_PATH_IMAGE026
，
in the formula (I), the compound is shown in the specification,
Figure 906815DEST_PATH_IMAGE027
when the discriminant Δ = B2The above formula presents a unique cut-off frequency ω when-4 AC =0cI.e. the case where the corresponding amplitude-frequency curve is tangent to 0 dB. At this time, the corresponding inertia control coefficient is the maximum inertia coefficient which is not influenced by time delay. To calculate this coefficient, the discriminant is expressed as KinExpression for the independent variables:
Figure 29491DEST_PATH_IMAGE028
，
in the formula (I), the compound is shown in the specification,
Figure 395882DEST_PATH_IMAGE029
。
according to the formula, the maximum inertia coefficient which is not influenced by time delay is obtained as follows:
Figure DEST_PATH_IMAGE030
，
Figure 250705DEST_PATH_IMAGE031
，
wherein, the first and the second end of the pipe are connected with each other,
Figure 561601DEST_PATH_IMAGE005
a first maximum inertia control coefficient; h is an inertia constant, and T is response time;
Figure 363335DEST_PATH_IMAGE001
is the damping ratio;
Figure 708866DEST_PATH_IMAGE002
is a natural frequency; d is the load frequency regulation factor, KGIs the primary frequency modulation droop coefficient of the generator, H is the inertia constant, T is the response time,
Figure 937853DEST_PATH_IMAGE006
。
when 0 is present<Kin<Kin_criAnd in time, the stability of the small disturbance frequency of the system is not influenced by time delay.
In step 103, setting inertia control coefficients based on the first inertia control coefficients and the model parameters, and determining the inertia control maximum delay constrained by small disturbance stability and the inertia control optimal delay constrained by large disturbance frequency stability corresponding to the set inertia control coefficients.
Preferably, the determining of the inertia control maximum delay constrained by small disturbance stability and the inertia control optimal delay constrained by large disturbance frequency stability corresponding to the set inertia control coefficient includes:
Figure DEST_PATH_IMAGE032
wherein the content of the first and second substances,
Figure 408148DEST_PATH_IMAGE008
controlling the maximum delay for the inertia corresponding to the set inertia control coefficient;
Figure 279152DEST_PATH_IMAGE009
controlling the coefficient for the set inertia;
Figure 479190DEST_PATH_IMAGE010
controlling optimal delay for inertia corresponding to the set inertia control coefficient;
Figure 879078DEST_PATH_IMAGE011
and
Figure 164566DEST_PATH_IMAGE012
the first cut-off frequency and the second cut-off frequency are respectively corresponding to the set inertia control coefficient;
Figure 573682DEST_PATH_IMAGE001
is the damping ratio;
Figure 769171DEST_PATH_IMAGE002
is a natural frequency; d is a load frequency adjusting coefficient; kGThe droop coefficient is the primary frequency modulation of the generator; h is an inertia constant; t is response time;
Figure 464594DEST_PATH_IMAGE013
the inverse of the response time T.
In the embodiment of the present invention, the first inertia amount control coefficient Kin_criAnd selecting and setting an inertia control coefficient between the model parameter H and the model parameter H, and then determining the inertia control maximum delay which is stably constrained by small disturbance and the inertia control optimal delay which is stably constrained by large disturbance frequency corresponding to the set inertia control coefficient.
When set Kin>Kin_criIn time, phase angle margin exists, the small disturbance stability of the system is influenced by time delay, two intersection points exist between the amplitude-frequency curve and 0dB at the moment, and the stable phase angle range is as follows:
Figure 112744DEST_PATH_IMAGE033
（k=0,1,2..），
wherein the content of the first and second substances,
Figure 184606DEST_PATH_IMAGE034
is the cut-off frequency.
At that time, the inertia control maximum delay constrained by small disturbance stability can be calculated as follows:
Figure 234601DEST_PATH_IMAGE035
，
Figure 366505DEST_PATH_IMAGE036
，
Figure 970793DEST_PATH_IMAGE037
，
Figure 111924DEST_PATH_IMAGE038
，
Figure 744988DEST_PATH_IMAGE039
，
wherein the content of the first and second substances,
Figure 47793DEST_PATH_IMAGE040
controlling the maximum delay for the inertia corresponding to the set inertia control coefficient;
Figure 670536DEST_PATH_IMAGE041
controlling the coefficient for the set inertia;
Figure 959566DEST_PATH_IMAGE011
a first cut-off frequency corresponding to the set inertia control coefficient;
Figure 843208DEST_PATH_IMAGE001
is the damping ratio;
Figure 192281DEST_PATH_IMAGE002
is a natural frequency; d is a load frequency adjusting coefficient; kGThe droop coefficient is the primary frequency modulation of the generator; h is an inertia constant; t is the response time.
In summary, at the inertia coefficient Kin（Kin_cri<Kin<H) In known conditions, the delay range is 0 under the stable constraint of small disturbance frequency<τin<τin_max。
At inertia control coefficient KinGreater case (K)in_cri<Kin<H) Then, the overshoot (maximum deviation of frequency) under the disturbance can be minimized by selecting an appropriate delay. The relationship between the optimal delay and the damping ratio and the overshoot are analyzed by a root locus method, and the delay link is reduced into the following steps by Taylor expansion:
Figure 161374DEST_PATH_IMAGE042
，
the inertia control link is as follows:
Figure 519674DEST_PATH_IMAGE043
，
drawing the dominant pole change locus according to the inertia control link formula, as shown in FIG. 7 (K)in=0.5, 1.5), it can be seen that as the delay increases, the damping ratio increases first and then decreases, and according to the negative correlation of the second order system overshoot and the damping ratio, the obtainable overshoot (maximum deviation of frequency) decreases first and then increases, as shown in fig. 8, at the inertia control coefficient KinAnd =1, the maximum deviation of the frequency increases and then decreases as the delay increases.
At inertia control coefficient KinGiven this knowledge, the optimal delay can be derived analytically. The cut-off frequency is substituted into the phase angle margin formula to obtain the phase angle margin with respect to the delay tauinIs described in (1). Suppose at KinIn the case of =2 (other parameters: H =3, K)G=20, T =1, D = 0), resulting in a cut-off frequency ωc1=1.52，ωc2=2.95, a phase angle margin can be further obtained as shown in fig. 9.
As the phase angle margin is smaller, the phase angle margin tends to increase first and then decrease as the delay increases. According to the automatic control theory, the phase angle margin and the damping ratio are in a direct proportion relation, and the damping ratio and the overshoot (the maximum frequency deviation) are in an inverse proportion relation, so that the phase angle margin and the overshoot are in an inverse proportion relation. Therefore, as the delay increases, the maximum deviation of the frequency decreases and then increases. In FIG. 9, the intersection point of the two curves is the maximum phase angle margin (corresponding to the optimal delay τ)in_opt) Therefore, the expression of the inertia control optimal delay corresponding to the set inertia control coefficient obtained by the simultaneous two equations is as follows:
Figure 257823DEST_PATH_IMAGE044
，
Figure 43376DEST_PATH_IMAGE045
，
Figure 375132DEST_PATH_IMAGE046
，
Figure 130598DEST_PATH_IMAGE047
，
Figure 864199DEST_PATH_IMAGE048
，
wherein the content of the first and second substances,
Figure 414129DEST_PATH_IMAGE049
controlling the maximum delay for the inertia corresponding to the set inertia control coefficient;
Figure 498760DEST_PATH_IMAGE050
controlling the coefficient for the set inertia;
Figure 57917DEST_PATH_IMAGE051
controlling optimal delay for inertia corresponding to the set inertia control coefficient;
Figure 380445DEST_PATH_IMAGE011
and
Figure 632435DEST_PATH_IMAGE012
the first cut-off frequency and the second cut-off frequency are respectively corresponding to the set inertia control coefficients;
Figure 673203DEST_PATH_IMAGE001
is the damping ratio;
Figure 770472DEST_PATH_IMAGE002
is a natural frequency; d is a load frequency adjusting coefficient; kGThe droop coefficient is the primary frequency modulation of the generator; h is an inertia constant; t is response time;
Figure 744244DEST_PATH_IMAGE013
the inverse of the response time T.
In step 105, inertia control delay time meeting frequency stability constraint is determined according to the inertia control maximum delay time and the inertia control optimal delay time.
Preferably, the determining an inertia control delay satisfying a frequency stability constraint according to the inertia control maximum delay and the inertia control optimal delay includes:
if the inertia control optimal delay is smaller than the inertia control maximum delay, determining inertia control delay meeting frequency stability constraint according to the inertia control optimal delay;
otherwise, determining the inertia control delay meeting the frequency stability constraint according to the inertia control maximum delay.
In the embodiment of the invention, the inertia control maximum delay tau constrained by small disturbance stability can be calculated according to the step 104in_maxThereby obtaining a delay range of 0<τin<τin_maxFrom step 105, the settings under large disturbances can be calculatedInertia control optimal delay tau corresponding to inertia control coefficientin_opt(ii) a If the optimal delay is in the stable delay range, taking inertia control delay meeting the frequency stability constraint as the optimal delay tau of inertia controlin_opt(ii) a If the optimal delay is not in the stable delay range, determining the inertia control delay meeting the frequency stability constraint as the maximum inertia control delay tauin_max。
The method of the invention stably determines the selection range of the inertia control parameters according to the small disturbance frequency, thereby inhibiting the frequency oscillation from occurring, and stably determines the optimal delay parameters according to the large disturbance frequency, thereby improving the maximum frequency deviation under disturbance to the maximum extent.
In the invention, based on a PSCAD simulation program, a 3-machine 9-node system is adopted to verify the method provided by the invention, and the generator 1 is replaced by a doubly-fed wind turbine generator with additional inertia control and droop control, as shown in FIG. 10, the primary frequency modulation aggregation parameter of a conventional generator is T =4.6s, KG=20。
When tau isinWhen =0.1s, the maximum inertia coefficient K is calculatedin_max=3.07, the frequency curve under different inertia control parameters is shown in fig. 11, and it can be seen that when the inertia coefficient K isin=0.5 (less than K)in_max) When the system is stable, as shown by a curve (r); when K isinWhen =4 (greater than K)in_max) Although the frequency deviation is reduced, the oscillation instability phenomenon occurs, and as shown by a curve II, the constant-amplitude oscillation is caused by the current limitation of a side converter of the fan rotor.
Calculating the maximum inertia coefficient K not affected by time delayin_cri=0.74, when Kin0.5 hour (less than K)in_cri) Even if the delay is large (tau)in=1 s), the system remains stable, as shown by curve c. When K isinWhen =3 (greater than K)in_cri) The maximum delay is calculated to be 0.9s when τinWhen =1s, the frequency oscillation is unstable as shown by curve r, and when τinWhen =0.1s, the system is stable (curve (r)), verifying the correctness of the proposed calculation method and the associated conclusions.
In the aspect of optimal delay, the optimal delay is calculated to be 1.15s, and the simulation is carried out through PSCADFrequency curve (K) at different delaysin= 2), as shown in fig. 12, it can be seen that as the delay increases, the maximum deviation of the frequency decreases first and then increases, when τ isinAnd when the frequency deviation is less than or equal to-0.435 Hz for 1.15s, the maximum frequency deviation is reduced by about 9 percent compared with-0.478 Hz without time delay, and the accuracy of the method is verified.
Fig. 13 is a block diagram of a system 1300 for determining an inertia control delay that satisfies a frequency stability constraint according to an embodiment of the invention. As shown in fig. 13, a system 1300 for determining inertia control delay satisfying a frequency stability constraint according to an embodiment of the present invention includes: the model building unit 1301, the first inertia amount control coefficient determining unit 1302, the maximum delay and optimal delay calculating unit 1303 and the delay determining unit 1304.
Preferably, the model establishing unit 1301 is configured to establish a system frequency response model including new energy inertia control and droop control, and determine a model parameter of the system frequency response model.
Preferably, wherein in the model establishing unit 1301, in the system frequency response model, the disturbance power Δ PdGenerating a frequency deviation delta f after the system frequency response; the new energy inertia control provides inertia support power delta P for the system according to the function of the frequency change rate of the systemin(ii) a The new energy droop control provides primary frequency modulation power delta P to the system according to the frequency deviation function of the systemdr(ii) a And after the new energy inertia support and the droop control act together, the unbalanced power of the system is reduced.
Preferably, in the model establishing unit 1301, the model parameters include: primary frequency modulation droop coefficient K of generatorGInertia constant H, load frequency regulation coefficient D, response time T, damping ratio
Figure 776922DEST_PATH_IMAGE001
And natural frequency
Figure 429621DEST_PATH_IMAGE002
(ii) a Wherein the content of the first and second substances,
Figure 471526DEST_PATH_IMAGE003
KG=1/R，
wherein R is a difference adjustment coefficient.
Preferably, the first inertia control coefficient determining unit 1302 is configured to calculate a first inertia control coefficient that is not affected by a delay time based on the model parameter.
Preferably, the first maximum inertia control coefficient determining unit 1302, according to the amplitude conditional expression, calculating a first maximum inertia control coefficient that is not affected by a delay includes:
Figure 158859DEST_PATH_IMAGE004
wherein the content of the first and second substances,
Figure 362439DEST_PATH_IMAGE005
a first maximum inertia control coefficient; h is an inertia constant, and T is response time;
Figure 502433DEST_PATH_IMAGE001
is the damping ratio;
Figure 816871DEST_PATH_IMAGE002
is a natural frequency; d is the load frequency regulation factor, KGIs the primary frequency modulation droop coefficient of the generator, H is the inertia constant, T is the response time,
Figure 358710DEST_PATH_IMAGE006
。
preferably, the maximum delay and optimal delay calculating unit 1303 is configured to set an inertia control coefficient based on the first inertia control coefficient and the model parameter, and determine an inertia control maximum delay that is stably constrained by a small disturbance and an inertia control optimal delay that is stably constrained by a large disturbance frequency, which correspond to the set inertia control coefficient.
Preferably, the determining, by the maximum delay and optimal delay calculating unit 1303, the inertia control maximum delay constrained by small disturbance stability and the inertia control optimal delay constrained by large disturbance frequency stability, which correspond to the set inertia control coefficient, includes:
Figure 992911DEST_PATH_IMAGE007
wherein the content of the first and second substances,
Figure 495568DEST_PATH_IMAGE008
controlling the maximum delay for the inertia corresponding to the set inertia control coefficient;
Figure 738330DEST_PATH_IMAGE009
controlling the coefficient for the set inertia;
Figure 10043DEST_PATH_IMAGE010
controlling optimal delay for inertia corresponding to the set inertia control coefficient;
Figure 680058DEST_PATH_IMAGE011
and
Figure 935590DEST_PATH_IMAGE012
the first cut-off frequency and the second cut-off frequency are respectively corresponding to the set inertia control coefficient;
Figure 982044DEST_PATH_IMAGE001
is the damping ratio;
Figure 108263DEST_PATH_IMAGE002
is a natural frequency; d is a load frequency adjusting coefficient; kGThe droop coefficient is the primary frequency modulation of the generator; h is an inertia constant; t is response time;
Figure 949180DEST_PATH_IMAGE013
the inverse of the response time T.
Preferably, the delay determining unit 1304 is configured to determine an inertia control delay meeting a frequency stability constraint according to the inertia control maximum delay and the inertia control optimal delay.
Preferably, the determining unit 1304, according to the inertia control maximum delay and the inertia control optimal delay, determines the inertia control delay meeting the frequency stability constraint, including:
if the inertia control optimal delay is smaller than the inertia control maximum delay, determining inertia control delay meeting frequency stability constraint according to the inertia control optimal delay;
otherwise, determining the inertia control delay meeting the frequency stability constraint according to the inertia control maximum delay.
The system 1300 for determining the inertia control delay satisfying the frequency stability constraint according to the embodiment of the present invention corresponds to the method 100 for determining the inertia control delay satisfying the frequency stability constraint according to another embodiment of the present invention, and is not described herein again.
The present invention provides a computer readable storage medium having stored thereon a computer program which, when executed by a processor, performs the steps of any of a method of determining an inertia control delay time that satisfies a frequency stability constraint.
The present invention provides an electronic device, including: the computer-readable storage medium described above; and
one or more processors to execute the program in the computer-readable storage medium.
The invention has been described with reference to a few embodiments. However, other embodiments of the invention than the one disclosed above are equally possible within the scope of the invention, as would be apparent to a person skilled in the art from the appended patent claims.
Generally, all terms used in the claims are to be interpreted according to their ordinary meaning in the technical field, unless explicitly defined otherwise herein. All references to "a/an/the [ device, component, etc ]" are to be interpreted openly as referring to at least one instance of said device, component, etc., unless explicitly stated otherwise. The steps of any method disclosed herein do not have to be performed in the exact order disclosed, unless explicitly stated.
As will be appreciated by one skilled in the art, embodiments of the present application may be provided as a method, system, or computer program product. Accordingly, the present application may take the form of an entirely hardware embodiment, an entirely software embodiment or an embodiment combining software and hardware aspects. Furthermore, the present application may take the form of a computer program product embodied on one or more computer-usable storage media (including, but not limited to, disk storage, CD-ROM, optical storage, and the like) having computer-usable program code embodied therein.
The present application is described with reference to flowchart illustrations and/or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of the application. It will be understood that each flow and/or block of the flow diagrams and/or block diagrams, and combinations of flows and/or blocks in the flow diagrams and/or block diagrams, can be implemented by computer program instructions. These computer program instructions may be provided to a processor of a general purpose computer, special purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, create means for implementing the functions specified in the flowchart flow or flows and/or block diagram block or blocks.
These computer program instructions may also be stored in a computer-readable memory that can direct a computer or other programmable data processing apparatus to function in a particular manner, such that the instructions stored in the computer-readable memory produce an article of manufacture including instruction means which implement the function specified in the flowchart flow or flows and/or block diagram block or blocks.
These computer program instructions may also be loaded onto a computer or other programmable data processing apparatus to cause a series of operational steps to be performed on the computer or other programmable apparatus to produce a computer implemented process such that the instructions which execute on the computer or other programmable apparatus provide steps for implementing the functions specified in the flowchart flow or flows and/or block diagram block or blocks.
Finally, it should be noted that: the above embodiments are only for illustrating the technical solutions of the present invention and not for limiting the same, and although the present invention is described in detail with reference to the above embodiments, those of ordinary skill in the art should understand that: modifications and equivalents may be made to the embodiments of the invention without departing from the spirit and scope of the invention, which is to be covered by the claims.

Claims (12)

1. A method of determining an inertia control delay that satisfies a frequency stability constraint, the method comprising:
establishing a system frequency response model containing new energy inertia control and droop control, and determining model parameters of the system frequency response model;
calculating a first inertia control coefficient which is not influenced by time delay based on the model parameters;
setting an inertia control coefficient based on the first inertia control coefficient and the model parameter, and determining the inertia control maximum delay which is stably constrained by small disturbance and the inertia control optimal delay which is stably constrained by large disturbance frequency corresponding to the set inertia control coefficient;
and determining the inertia control delay meeting the frequency stability constraint according to the inertia control maximum delay and the inertia control optimal delay.
2. The method of claim 1, wherein the model parameters comprise: primary frequency modulation droop coefficient K of generatorGInertia constant H, load frequency regulation coefficient D, response time T, damping ratio
Figure 72018DEST_PATH_IMAGE001
And natural frequency
Figure DEST_PATH_IMAGE002
(ii) a Wherein the content of the first and second substances,
Figure 926841DEST_PATH_IMAGE003
KG=1/R，
wherein R is a difference adjustment coefficient.
3. The method according to claim 1, wherein calculating a first maximum inertia control coefficient that is not affected by a delay time according to the magnitude conditional expression includes:
Figure DEST_PATH_IMAGE004
，
Figure 847524DEST_PATH_IMAGE005
，
Figure DEST_PATH_IMAGE006
，
Figure 445996DEST_PATH_IMAGE007
，
wherein the content of the first and second substances,
Figure DEST_PATH_IMAGE008
a first maximum inertia control coefficient; h is an inertia constant, and T is response time;
Figure 401313DEST_PATH_IMAGE001
is the damping ratio;
Figure 692617DEST_PATH_IMAGE002
is a natural frequency; d is the load frequency regulation factor, KGDroop coefficient for primary frequency modulation of generatorH is an inertia constant, T is a response time,
Figure 428492DEST_PATH_IMAGE009
。
4. the method according to claim 1, wherein the determining of the inertia control maximum delay constrained by small disturbance stability and the inertia control optimal delay constrained by large disturbance frequency stability corresponding to the set inertia control coefficient comprises:
Figure DEST_PATH_IMAGE010
wherein the content of the first and second substances,
Figure 565075DEST_PATH_IMAGE011
controlling the maximum delay for the inertia corresponding to the set inertia control coefficient;
Figure 968375DEST_PATH_IMAGE013
controlling the coefficient for the set inertia;
Figure DEST_PATH_IMAGE014
controlling optimal delay for inertia corresponding to the set inertia control coefficient;
Figure 899422DEST_PATH_IMAGE015
and
Figure DEST_PATH_IMAGE016
the first cut-off frequency and the second cut-off frequency are respectively corresponding to the set inertia control coefficient;
Figure 788837DEST_PATH_IMAGE017
is the damping ratio;
Figure DEST_PATH_IMAGE018
is a natural frequency; d is negativeA charge frequency adjustment coefficient; kGThe droop coefficient is the primary frequency modulation of the generator; h is an inertia constant; t is response time;
Figure 463532DEST_PATH_IMAGE019
the inverse of the response time T.
5. The method of claim 1, wherein determining an inertia control delay that satisfies a frequency stability constraint based on the inertia control maximum delay and the inertia control optimal delay comprises:
if the inertia control optimal delay is smaller than the inertia control maximum delay, determining inertia control delay meeting frequency stability constraint according to the inertia control optimal delay;
otherwise, determining the inertia control delay meeting the frequency stability constraint according to the inertia control maximum delay.
6. A system for determining an inertia control delay that satisfies a frequency stability constraint, the system comprising:
the model establishing unit is used for establishing a system frequency response model containing new energy inertia control and droop control and determining model parameters of the system frequency response model;
the first inertia control coefficient determining unit is used for calculating a first inertia control coefficient which is not influenced by time delay based on the model parameters;
the maximum delay and optimal delay calculation unit is used for setting an inertia control coefficient based on the first inertia control coefficient and the model parameter, and determining the inertia control maximum delay which is stably constrained by small disturbance and the inertia control optimal delay which is stably constrained by large disturbance frequency corresponding to the set inertia control coefficient;
and the delay determining unit is used for determining the inertia control delay meeting the frequency stability constraint according to the inertia control maximum delay and the inertia control optimal delay.
7. According to claimThe system of claim 6, wherein at the model building unit, the model parameters comprise: primary frequency modulation droop coefficient K of generatorGInertia constant H, load frequency regulation coefficient D, response time T, damping ratio
Figure 721338DEST_PATH_IMAGE001
And natural frequency
Figure 620024DEST_PATH_IMAGE002
(ii) a Wherein the content of the first and second substances,
Figure 533753DEST_PATH_IMAGE003
KG=1/R，
wherein R is a difference adjustment coefficient.
8. The system according to claim 6, wherein the first maximum inertia control coefficient determining unit calculates a first maximum inertia control coefficient that is not affected by a delay time according to the magnitude conditional expression, including:
Figure 277719DEST_PATH_IMAGE004
，
Figure 390031DEST_PATH_IMAGE005
，
Figure 459618DEST_PATH_IMAGE006
，
Figure 860644DEST_PATH_IMAGE007
，
wherein the content of the first and second substances,
Figure 408300DEST_PATH_IMAGE008
a first maximum inertia control coefficient; h is an inertia constant, and T is response time;
Figure 375119DEST_PATH_IMAGE001
is the damping ratio;
Figure 881186DEST_PATH_IMAGE002
is a natural frequency; d is the load frequency regulation factor, KGIs the primary frequency modulation droop coefficient of the generator, H is the inertia constant, T is the response time,
Figure 300666DEST_PATH_IMAGE009
。
9. the system of claim 6, wherein the maximum delay and optimal delay calculation unit,
determining the inertia control maximum delay constrained by small disturbance stability and the inertia control optimal delay constrained by large disturbance frequency stability corresponding to the set inertia control coefficient, comprising:
Figure DEST_PATH_IMAGE020
wherein the content of the first and second substances,
Figure 324117DEST_PATH_IMAGE011
controlling the maximum delay for the inertia corresponding to the set inertia control coefficient;
Figure 145443DEST_PATH_IMAGE013
controlling the coefficient for the set inertia;
Figure 822412DEST_PATH_IMAGE014
controlling optimal delay for inertia corresponding to the set inertia control coefficient;
Figure 932450DEST_PATH_IMAGE015
and
Figure 821909DEST_PATH_IMAGE016
the first cut-off frequency and the second cut-off frequency are respectively corresponding to the set inertia control coefficient;
Figure 763320DEST_PATH_IMAGE017
is the damping ratio;
Figure 345611DEST_PATH_IMAGE018
is a natural frequency; d is a load frequency adjusting coefficient; kGThe droop coefficient is the primary frequency modulation of the generator; h is an inertia constant; t is response time;
Figure 5262DEST_PATH_IMAGE019
the inverse of the response time T.
10. The system of claim 6, wherein the delay determining unit determines the inertia control delay satisfying a frequency stability constraint according to the inertia control maximum delay and the inertia control optimal delay, and comprises:
if the inertia control optimal delay is smaller than the inertia control maximum delay, determining inertia control delay meeting frequency stability constraint according to the inertia control optimal delay;
otherwise, determining the inertia control delay meeting the frequency stability constraint according to the inertia control maximum delay.
11. A computer-readable storage medium, on which a computer program is stored which, when being executed by a processor, carries out the steps of the method according to any one of claims 1 to 5.
12. An electronic device, comprising:
the computer-readable storage medium recited in claim 11; and
one or more processors to execute the program in the computer-readable storage medium.
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