CN104747294A - Gas turbine fuel pressure control method and gas turbine fuel pressure control system - Google Patents

Gas turbine fuel pressure control method and gas turbine fuel pressure control system Download PDF

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Publication number
CN104747294A
CN104747294A CN201510036626.2A CN201510036626A CN104747294A CN 104747294 A CN104747294 A CN 104747294A CN 201510036626 A CN201510036626 A CN 201510036626A CN 104747294 A CN104747294 A CN 104747294A
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value
variable quantity
error
parameter variable
gas turbine
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CN104747294B (en
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赵碧徽
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China United Heavy Gas Turbine Technology Co Ltd
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Beijing Huatsing Gas Turbine and IGCC Technology Co Ltd
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Abstract

The invention relates to a gas turbine fuel pressure control method and a gas turbine fuel pressure control system. The method comprises the following steps: S1. comparing a pressure reference value with a pressure measured value to obtain a pressure error, and carrying out differential operation on the pressure error to obtain a change rate of the error; S2. carrying out blurring operation on the error and the change rate of the error to obtain a PID parameter variation; S3. correcting an original PID parameter value according to the PID parameter variation to obtain a corrected PID parameter value; S4. carrying out PID operation according to the corrected PID parameter value to obtain target valve opening; and S5. regulating the opening degree of a speed ratio valve according to the target valve opening and actual valve opening. By combining blurring control with PID, the adaptability and the robustness of pressure control are improved, the parameter self-tuning is achieved, and when control parameters in a gas turbine are changed, the pressure of the gas turbine still can be regulated accurately, so that a good control effect can be obtained.

Description

Gas turbine fuel compress control method and system
Technical field
The present invention relates to gas turbine technology field, in particular to a kind of gas turbine pressure controlling method and a kind of gas turbine pressure control system.
Background technique
Gas turbine is using gas, liquid as fuel, and the heat energy discharged during fuel combustion is become useful work, the impeller type dynamic power machine of energy high speed rotary.It controls rotating speed, the rising of load or reduction by changing fuel quantity.And the adjustment of fuel quantity is jointly completed by speed ratio valve and control valve, speed ratio pressure regulating valve, control valve adjust flux.In order to after full speed zero load, only regulate by changing control valve aperture the flow entering firing chamber, then control upstream pressure and should remain constant, namely speed ratio valve regulation should make fuel pressure remained constant after its valve.
Due to the system that gas turbine control system is a multivariable, strong jamming and parameter time varying, simultaneously, tradition pid parameter is in the process of adjusting, its setting valve has the optimal value of certain area, instead of the optimum value of the overall situation, therefore can not from the contradiction in fact solving dynamic quality and stable state accuracy.Thus, in fuel pressure control system, traditional PID control is adopted can not to reach desirable control effects.
Summary of the invention
Technical problem to be solved by this invention is, how to improve the control effects to gas turbine pressure.
For this purpose, the present invention proposes a kind of gas turbine fuel compress control method, comprising:
S1, compares compression force reference value and pressure measuring value, obtains pressure error, and differentiating to described pressure error obtains error rate;
S2, carries out fuzzy operation to described error and error rate, obtains pid parameter variable quantity;
S3, revises original pid parameter value according to described pid parameter variable quantity, obtains revising pid parameter value;
S4, carries out PID arithmetic according to described correction pid parameter value, obtains target valve aperture;
S5, according to the aperture of described target valve aperture and actual valve aperture adjusting speed ratio valve.
Preferably, described pid parameter variable quantity comprises scale parameter variable quantity, integral parameter variable quantity and differential parameter variable quantity.
Preferably, described step S2 comprises:
S21, judges the absolute value of described error and the magnitude relationship of the first predefined value and the second predefined value, and wherein, described first predefined value is less than described second predefined value;
S22, if the absolute value of described error is greater than the second predefined value, then in the scope being greater than the second selected value, choose described scale parameter variable quantity, and in the scope being less than the first selected value, choose described integral parameter variable quantity and differential parameter variable quantity, wherein, described first selected value is less than described second selected value;
S23, if the absolute value of described error is greater than described first predefined value and be less than described second predefined value, then chooses described scale parameter variable quantity, integral parameter variable quantity and differential parameter variable quantity between described first selected value and the second selected value;
S24, if the absolute value of described error is less than described first predefined value, then in the scope being greater than described second selected value, choose described scale parameter variable quantity and integral parameter variable quantity, and when the absolute value of described error rate is greater than described second predefined value, described differential parameter variable quantity is chosen in the scope being less than described first selected value, when the absolute value of described error rate is less than described first predefined value, in the scope being greater than described second selected value, choose described differential parameter variable quantity.
Preferably, described step S1 comprises: pressure transducer obtains the downstream pressure of speed ratio valve as described pressure measuring value.
Preferably, described step S5 comprises: position transmitter obtains the real-time opening value of described speed ratio valve as described actual opening value.
The invention allows for a kind of gas turbine fuel control pressurer system, comprising:
Pressure transducer, obtains pressure measuring value for the downstream pressure measuring speed ratio valve;
Position transmitter, for measuring the actual valve aperture of speed ratio valve;
Fuzzy Calculation unit, for compression force reference value and pressure measuring value are compared, obtain pressure error, described pressure error is differentiated and obtains error rate, fuzzy operation is carried out to described error and error rate, obtains pid parameter variable quantity, according to described pid parameter variable quantity, original pid parameter value is revised, obtain revising pid parameter value, carry out PID arithmetic according to described correction pid parameter value, obtain target valve aperture;
Servomechanism, for the aperture according to described target valve aperture and actual valve aperture adjusting speed ratio valve.
Pass through technique scheme, fuzzy control can be combined with PID, improve pressure controlled adaptability and robustness, realize parameter self-tuning, when controling parameters changes in the gas turbine, still accurately can regulate the pressure of gas turbine, thus obtain better control effects.
Accompanying drawing explanation
Can understanding the features and advantages of the present invention clearly by reference to accompanying drawing, accompanying drawing is schematic and should not be construed as and carry out any restriction to the present invention, in the accompanying drawings:
Fig. 1 shows the schematic flow diagram of gas turbine fuel compress control method according to an embodiment of the invention;
Fig. 2 shows the principle schematic of gas turbine fuel compress control method according to an embodiment of the invention;
Fig. 3 shows the pressure controlled structural representation of gas turbine fuel according to an embodiment of the invention;
Fig. 4 shows pid parameter variable quantity according to an embodiment of the invention and chooses schematic flow diagram;
Fig. 5 shows the pressure controlled fuzzy algorithmic approach schematic diagram of gas turbine fuel according to an embodiment of the invention;
Fig. 6 shows the principle schematic of gas turbine fuel compress control method according to an embodiment of the invention.
Embodiment
In order to more clearly understand above-mentioned purpose of the present invention, feature and advantage, below in conjunction with the drawings and specific embodiments, the present invention is further described in detail.It should be noted that, when not conflicting, the feature in the embodiment of the application and embodiment can combine mutually.
Set forth a lot of detail in the following description so that fully understand the present invention; but; the present invention can also adopt other to be different from other modes described here and implement, and therefore, protection scope of the present invention is not by the restriction of following public specific embodiment.
As shown in Figure 1, gas turbine fuel compress control method according to an embodiment of the invention, comprising:
S1, compares compression force reference value and pressure measuring value, obtains pressure error, and differentiating to pressure error obtains error rate;
S2, carries out fuzzy operation to error and error rate, obtains pid parameter variable quantity;
S3, revises original pid parameter value according to pid parameter variable quantity, obtains revising pid parameter value;
S4, carries out PID arithmetic according to correction pid parameter value, obtains target valve aperture;
S5, according to the aperture of target valve aperture and actual valve aperture adjusting speed ratio valve.
Fuel pressure controls to realize mainly through two closed loop controls, wherein step S1 to S4 can control as outer shroud, mainly realize in software, step S5 controls as inner ring, mainly complete within hardware, Comprehensive Control can be carried out according to the result that inner ring controls and outer shroud controls to obtain to speed ratio valve, thus reach control effects more accurately.The principle of two closed loop controls as shown in Figure 2.
Calculate pid parameter variable quantity by fuzzy algorithmic approach to revise pid parameter value, parameter in PID arithmetic can be made with systematic error and error rate dynamic change, more meet rule and the characteristic of parameter real-time change in work.Various factors can be considered in control procedure, improve control performance with maximum possible, namely reduce the response time of control and reduce overshoot, and the precision controlled is improved.
And can play the advantage of PID and fuzzy control in control procedure, applicability is stronger, and robustness is better, when parameter changes especially in systems in which, the control effects of realization more can meet actual control needs.
As shown in Figure 3, preferably, pid parameter variable quantity comprises scale parameter variable quantity, integral parameter variable quantity and differential parameter variable quantity.Wherein, scale parameter variable quantity, integral parameter variable quantity and differential parameter variable quantity are respectively Δ k p, Δ k i, Δ k d, corresponding scale parameter, integral parameter and differential parameter are respectively k p, k i, k d, pressure error is e, and error rate is .
Wherein, fuzzy operation can have been come by MATLAB, and MATLAB and gas turbine control system are by opc server communication, and the effect of opc server is the bridge of communication between MATLAB and gas turbine own control systems, the exchanges data of both realizations.Comparatively complicated FUZZY ALGORITHMS FOR CONTROL is realized by MATLAB, without the need to additionally increasing software in the gas turbine, even the part controlling functions of original for gas turbine software can be transferred to MATLAB, to alleviate the program operating pressure of gas turbine, improve control performance.
As shown in Figure 4, preferably, step S2 comprises:
S21, the absolute value of error in judgement and the magnitude relationship of the first predefined value and the second predefined value, wherein, the first predefined value is less than the second predefined value;
S22, if the absolute value of error is greater than the second predefined value, then in the scope being greater than the second selected value, choose scale parameter variable quantity, and in the scope being less than the first selected value, choose integral parameter variable quantity and differential parameter variable quantity, wherein, the first selected value is less than the second selected value;
S23, if the absolute value of error is greater than the first predefined value and be less than the second predefined value, then chooses scale parameter variable quantity, integral parameter variable quantity and differential parameter variable quantity between the first selected value and the second selected value;
S24, if the absolute value of error is less than the first predefined value, then in the scope being greater than the second selected value, choose scale parameter variable quantity and integral parameter variable quantity, and when the absolute value of error rate is greater than the second predefined value, differential parameter variable quantity is chosen in the scope being less than the first selected value, when the absolute value of error rate is less than the first predefined value, in the scope being greater than the second selected value, choose differential parameter variable quantity.
As shown in Figure 5, error e obtains error rate through differential to the processing procedure of fuzzy algorithmic approach , by determine e and domain and corresponding membership function obtain inputting fuzzy variable, determine the domain of output variable simultaneously; Then according to pid parameter on the impact of systematic function and the different phase at system dynamic response, the Adjustment principle of pid parameter, obtains the fuzzy rule that the pid parameter of system responses the best can be made to adjust; Carry out fuzzy reasoning, obtain Parameters variation amount, draw accurate Parameters variation amount Δ k by anti fuzzy method method p, Δ k i, Δ k d, then obtain Δ k by fuzzy algorithmic approach p, Δ k i, Δ k dafterwards the former pid parameter value in control system is revised, obtain revising pid parameter value k p, k i, k d
k p＝k′ p+Δk p
k i＝k i′+Δk i
k d＝k′ d+Δk d
Wherein, k p', k i', k d' be pid parameter value in a upper timing control system, initial time pid parameter value adopts conventional setting method to obtain pre-tuning value.Carry out PID arithmetic after parameters revision, the final output of controller is:
u = k p e + k i ∫ edt + k d de dt
Wherein u is target valve aperture.
Main according to coming Parameters variation amount Δ k the judgement of Error Absolute Value below p, Δ k i, Δ k dvalue be described.
Error | when e| is larger, the absolute value of specification error is comparatively large, no matter the variation tendency of error, all should consider the Δ k of controller pget higher value, to improve the rapidity of response; And be prevent because | the instantaneous excessive differential supersaturation that may occur of e|, Δ k dless value should be got; For controlling overshoot, Δ k ialso should value very little.
When error | e|, when median size, for ensureing the speed of response of system and controlling overshoot, should reduce Δ k p, Δ k i, Δ k dshould be moderate.
When error | when e| is less, for ensureing that system has good steady-state characteristic, Δ k should be strengthened p, Δ k ivalue, producing vibration for avoiding simultaneously, and considering the interference free performance of system, Δ k dvalue should be with connect, when Δ k time large dget little, when hour Δ k dget large.
Preferably, step S1 comprises: pressure transducer obtains the downstream pressure of speed ratio valve as pressure measuring value.
Preferably, step S5 comprises: position transmitter obtains the real-time opening value of speed ratio valve as actual opening value.
As shown in Figure 6, the invention allows for a kind of gas turbine fuel control pressurer system 10, comprising:
Pressure transducer 11, obtains pressure measuring value for the downstream pressure measuring speed ratio valve;
Position transmitter 12, for measuring the actual valve aperture of speed ratio valve;
Fuzzy Calculation unit 13, for compression force reference value and pressure measuring value are compared, obtain pressure error, pressure error is differentiated and obtains error rate, fuzzy operation is carried out to error and error rate, obtains pid parameter variable quantity, according to pid parameter variable quantity, original pid parameter value is revised, obtain revising pid parameter value, carry out PID arithmetic according to correction pid parameter value, obtain target valve aperture;
Servomechanism 14, for the aperture according to target valve aperture and actual valve aperture adjusting speed ratio valve.
More than be described with reference to the accompanying drawings technological scheme of the present invention, consider in correlation technique, traditional pid parameter is in the process of adjusting, and its setting valve has the optimal value of certain area, instead of the optimum value of the overall situation, therefore can not from the contradiction in fact solving dynamic quality and stable state accuracy.By the technological scheme of the application, fuzzy control can be combined with PID, improve pressure controlled adaptability and robustness, realize parameter self-tuning, when controling parameters changes in the gas turbine, still accurately can regulate the pressure of gas turbine, thus obtain better control effects.
In the present invention, term " first ", " second " only for describing object, and can not be interpreted as instruction or hint relative importance.Term " multiple " refers to two or more, unless otherwise clear and definite restriction.
The foregoing is only the preferred embodiments of the present invention, be not limited to the present invention, for a person skilled in the art, the present invention can have various modifications and variations.Within the spirit and principles in the present invention all, any amendment done, equivalent replacement, improvement etc., all should be included within protection scope of the present invention.

Claims (6)

1. a gas turbine fuel compress control method, is characterized in that, comprising:
S1, compares compression force reference value and pressure measuring value, obtains pressure error, and differentiating to described pressure error obtains error rate;
S2, carries out fuzzy operation to described error and error rate, obtains pid parameter variable quantity;
S3, revises original pid parameter value according to described pid parameter variable quantity, obtains revising pid parameter value;
S4, carries out PID arithmetic according to described correction pid parameter value, obtains target valve aperture;
S5, according to the aperture of described target valve aperture and actual valve aperture adjusting speed ratio valve.
2. gas turbine fuel compress control method according to claim 1, is characterized in that,
Described pid parameter variable quantity comprises scale parameter variable quantity, integral parameter variable quantity and differential parameter variable quantity.
3. gas turbine fuel compress control method according to claim 2, it is characterized in that, described step S2 comprises:
S21, judges the absolute value of described error and the magnitude relationship of the first predefined value and the second predefined value, and wherein, described first predefined value is less than described second predefined value;
S22, if the absolute value of described error is greater than the second predefined value, then chooses described scale parameter variable quantity, and in the scope being less than the first selected value, chooses described integral parameter variable quantity and differential parameter variable quantity in the scope being greater than the second selected value;
S23, if the absolute value of described error is greater than described first predefined value and be less than described second predefined value, then between described first selected value and the second selected value, choose described scale parameter variable quantity, integral parameter variable quantity and differential parameter variable quantity, wherein, described first selected value is less than described second selected value;
S24, if the absolute value of described error is less than described first predefined value, then in the scope being greater than described second selected value, choose described scale parameter variable quantity and integral parameter variable quantity, and when the absolute value of described error rate is greater than described second predefined value, described differential parameter variable quantity is chosen in the scope being less than described first selected value, when the absolute value of described error rate is less than described first predefined value, in the scope being greater than described second selected value, choose described differential parameter variable quantity.
4. gas turbine fuel compress control method according to claim 1, it is characterized in that, described step S1 comprises: pressure transducer obtains the downstream pressure of speed ratio valve as described pressure measuring value.
5. gas turbine fuel compress control method according to claim 1, it is characterized in that, described step S5 comprises: position transmitter obtains the real-time opening value of described speed ratio valve as described actual opening value.
6. a gas turbine fuel control pressurer system, is characterized in that, comprising:
Pressure transducer, obtains pressure measuring value for the downstream pressure measuring speed ratio valve;
Position transmitter, for measuring the actual valve aperture of speed ratio valve;
Fuzzy Calculation unit, for compression force reference value and pressure measuring value are compared, obtain pressure error, described pressure error is differentiated and obtains error rate, fuzzy operation is carried out to described error and error rate, obtains pid parameter variable quantity, according to described pid parameter variable quantity, original pid parameter value is revised, obtain revising pid parameter value, carry out PID arithmetic according to described correction pid parameter value, obtain target valve aperture;
Servomechanism, for the aperture according to described target valve aperture and actual valve aperture adjusting speed ratio valve.
CN201510036626.2A 2015-01-23 2015-01-23 Gas turbine fuel compress control method and system Active CN104747294B (en)

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CN109976145A (en) * 2019-04-16 2019-07-05 新奥能源动力科技（上海）有限公司 The method of pid parameter, master controller in regulating gas turbine master controller
CN110010931A (en) * 2019-03-25 2019-07-12 嘉兴德燃动力系统有限公司 A kind of control strategy method and system of fuel battery engines hydrogen supply subsystem
CN110080885A (en) * 2019-04-16 2019-08-02 新奥能源动力科技（上海）有限公司 A kind of method and device controlling gas turbine
CN112817229A (en) * 2021-03-16 2021-05-18 昆明理工大学 Automatic machine learning system and method applied to pressure precision control
CN112963339A (en) * 2021-03-26 2021-06-15 北京氢澜科技有限公司 Air compressor rotating speed control method, device and equipment based on multi-mode PID
CN113281990A (en) * 2021-05-24 2021-08-20 无锡威孚高科技集团股份有限公司 Pressure control method, device and system for DPF testing

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110010931A (en) * 2019-03-25 2019-07-12 嘉兴德燃动力系统有限公司 A kind of control strategy method and system of fuel battery engines hydrogen supply subsystem
CN109976145A (en) * 2019-04-16 2019-07-05 新奥能源动力科技（上海）有限公司 The method of pid parameter, master controller in regulating gas turbine master controller
CN110080885A (en) * 2019-04-16 2019-08-02 新奥能源动力科技（上海）有限公司 A kind of method and device controlling gas turbine
CN110080885B (en) * 2019-04-16 2020-05-26 新奥能源动力科技（上海）有限公司 Method and device for controlling gas turbine and storage medium
CN109976145B (en) * 2019-04-16 2022-03-25 新奥能源动力科技（上海）有限公司 Method for adjusting PID parameters, main controller and storage medium
CN112817229A (en) * 2021-03-16 2021-05-18 昆明理工大学 Automatic machine learning system and method applied to pressure precision control
CN112817229B (en) * 2021-03-16 2023-03-07 昆明理工大学 Automatic machine learning system and method applied to pressure precision control
CN112963339A (en) * 2021-03-26 2021-06-15 北京氢澜科技有限公司 Air compressor rotating speed control method, device and equipment based on multi-mode PID
CN113281990A (en) * 2021-05-24 2021-08-20 无锡威孚高科技集团股份有限公司 Pressure control method, device and system for DPF testing

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Patentee before: Beijing Huatsing Gas Turbine & IGCC Technology Co., Ltd.

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