CN113688510B - Surge prediction method of centrifugal compression system for fuel cell vehicle - Google Patents
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Abstract
The invention relates to a surge prediction method of a centrifugal compression system for a fuel cell vehicle, which comprises the following steps: constructing a pneumatic performance analysis model of the centrifugal compressor for the fuel cell vehicle to obtain the pressure ratio characteristic of the centrifugal compressor; based on a Moore-Greitzer surge model, combining the pressure ratio characteristic of a centrifugal compressor to establish a surge aerodynamic model of the centrifugal compression system; obtaining pressure oscillation under the surge working condition of the centrifugal compressor through test measurement, and carrying out fast Fourier transform on the pressure oscillation to obtain surge frequency; carrying out parameter identification on a surge aerodynamic model by utilizing the surge frequency; fitting the rotating speed and the identified parameters to obtain a surge model of the centrifugal compression system under the working condition of full rotating speed; and inputting the rotation speed of the centrifugal compressor and the opening of the throttle valve into a surge model of the centrifugal compression system, and outputting a corresponding surge prediction result. Compared with the prior art, the method can rapidly and accurately predict the surge characteristics of the centrifugal compression system on the premise of not depending on a large number of surge tests of the centrifugal compressor.
Description
Technical Field
The invention relates to the technical field of research on surge characteristics of centrifugal compression systems, in particular to a surge prediction method of a centrifugal compression system for a fuel cell vehicle.
Background
With the commercialization and popularization of fuel cell automobiles, the fuel cell industry has rapidly developed. For fuel cell systems, an air compressor is a critical component that can provide pressurized air to the fuel cell system to increase the efficiency and specific power of the fuel cell stack. At present, a centrifugal compressor is one of the best choices of air compressors for fuel cell vehicles, so most of the mainstream fuel cell air assist systems for vehicles adopt the centrifugal compressor. However, the centrifugal compressor is easy to surge under the working condition of low mass flow, even causes system damage in severe cases, and the surge can greatly influence the stable working range of the centrifugal compressor. Centrifugal compressors cannot operate for a long time or frequently under a surge condition, and if the surge characteristics are studied through a large number of tests, risks are necessarily brought to test personnel and equipment. In order to study the surge characteristics and design an active surge control strategy, it is necessary to predict the surge process of a centrifugal compression system for a fuel cell vehicle.
Chinese patent CN107924425a proposes a method for predicting surge in a compressor, which can predict the surge boundary of the compressor more accurately, but cannot reflect the surge characteristics of the compression system, such as the frequency and amplitude of pressure oscillation, and meanwhile, the method needs to build a Computational Fluid Dynamics (CFD) simulation model of the compressor to perform numerical simulation, has extremely high requirements on computational resources, and is difficult to be used as a model foundation for designing an active surge control strategy. Chinese patent CN110848166a proposes a method for predicting surge frequency of an axial compressor, which avoids experimental measurement, and is mainly aimed at an axial compressor, and the prediction result of the method is very dependent on structural parameters of a compression system, and early determination of these parameters is difficult, so that it is difficult to accurately predict surge characteristics, and thus it cannot be used as a model base for designing an active surge control strategy of a centrifugal compression system.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a surge prediction method of a centrifugal compression system for a fuel cell vehicle, so as to rapidly and accurately predict the surge characteristics of the centrifugal compression system on the premise of not depending on a large number of surge tests of the centrifugal compressor.
The aim of the invention can be achieved by the following technical scheme: a surge prediction method of a centrifugal compression system for a fuel cell vehicle comprises the following steps:
s1, constructing a pneumatic performance analysis model of a centrifugal compressor for a fuel cell vehicle to obtain the pressure ratio characteristic of the centrifugal compressor;
s2, based on a Moore-Greitzer surge model, combining the pressure ratio characteristics of the centrifugal compressor obtained in the step S1 to establish a surge aerodynamic model of the centrifugal compression system;
s3, obtaining pressure oscillation under the surge working condition of the centrifugal compressor through test measurement, and performing fast Fourier transform on the pressure oscillation to obtain surge frequency;
carrying out parameter identification on the surge aerodynamic model established in the step S2 by utilizing the surge frequency;
fitting the rotating speed and the identified parameters to obtain a surge model of the centrifugal compression system under the working condition of full rotating speed;
s4, inputting the rotation speed of the centrifugal compressor and the opening of the throttle valve into a surge model of the centrifugal compression system, outputting to obtain corresponding dynamic mass flow and gas pressure, and obtaining a surge prediction result.
Further, the step S1 is specifically implemented by constructing a pneumatic performance analysis model of the centrifugal compressor to obtain a centrifugal compressor pressure ratio ψ (m c ω) and mass flow m c And the rotational speed omega.
Further, the step S2 specifically includes the following steps:
s21, establishing a Moore-Greitzer surge model according to the pressure ratio characteristic of the centrifugal compressor obtained in the step S1;
s22, correcting the Moore-Greitzer surge model to obtain a centrifugal compression system surge aerodynamic model.
Further, the step S22 specifically considers the influence of the outlet gas temperature on the sound velocity under different working conditions of the centrifugal compressor, and simultaneously introduces the correction volume of the centrifugal compression system into the Moore-Greitzer surge model to correct the Moore-Greitzer surge model.
Further, the Moore-Greitzer surge model established in the step S21 is specifically:
wherein p is p To compress the pressure of the system cavity, p 0 Is the external environmental pressure, V p To compress the volume of the system cavity, a 0 Is the sound velocity, k t Is the characteristic parameter of the electromagnetic valve, A is the area of the compressor, L c To compress the system tubing length.
Further, the influence of the outlet gas temperature of the centrifugal compressor under different working conditions on the sound velocity is specifically represented by the following formula:
wherein T is out For the outlet gas temperature of the centrifugal compressor, T in The inlet gas temperature of the centrifugal compressor, γ is the specific heat ratio.
Further, the correction volume of the centrifugal compression system is specifically:
ΔV p ＝V p -L c ×A 1
wherein A is 1 To compress the system cavity pressure, deltaV p To correct the volume.
Further, the step S3 specifically uses the surge frequency to identify the corrected volume in the surge aerodynamic model established in the step S2.
Further, the step S3 specifically includes the following steps:
s31, obtaining pressure oscillation of the centrifugal compressor in surge under different rotating speed working conditions through test measurement;
s32, performing fast Fourier transform on the measured pressure oscillation data to obtain corresponding surge frequency;
s33, identifying a correction volume in a surge aerodynamic model according to the surge frequency;
s34, based on the identified correction volume, further fitting to obtain a relation expression of the correction volume and the rotating speed, and substituting the relation expression into a surge aerodynamic model to obtain the surge model of the centrifugal compression system under the working condition of full rotating speed.
Further, in step S34, a polynomial fitting method is specifically adopted to obtain a relation expression of the corrected volume and the rotation speed.
Compared with the prior art, the invention has the following advantages:
1. according to the invention, the pressure ratio characteristic of the centrifugal compressor is obtained by establishing the pneumatic performance analysis model of the centrifugal compressor, the traditional Moore-Greitzer surge model is combined, the surge aerodynamic model is corrected, the parameters of the surge aerodynamic model can be identified by only measuring the pressure oscillation of the centrifugal compressor through a test, the fitting relation between the parameters and the rotating speed is obtained through the combination of the identification, and the surge model of the centrifugal compression system under the working condition of full rotating speed is further obtained, so that the requirement on computing resources is greatly reduced, and meanwhile, a large number of surge tests of the centrifugal compression system are not required, so that an accurate surge model can be quickly established, and the subsequent rapid and accurate prediction of the surge process of the centrifugal compression system is ensured.
2. According to the invention, the pressure oscillation of the centrifugal compressor in surging under different rotating speed working conditions is obtained through test measurement, then the pressure oscillation is subjected to fast Fourier transform to obtain the corresponding oscillation frequency, and the correction parameters in the surging aerodynamic model can be identified by utilizing the oscillation frequency, so that a large number of surging tests of the centrifugal compression system are not needed to identify the parameters, and the centrifugal compressor can be prevented from running under the surging working conditions for a long time or frequently, so that the safety of test personnel and equipment is ensured.
3. According to the invention, the influence of outlet gas temperature on sound velocity under different working conditions of the centrifugal compressor is considered, and meanwhile, the correction volume of the centrifugal compression system is introduced into the surge model, so that the Moore-Greitzer surge model is corrected, and the surge aerodynamic model of the centrifugal compression system is obtained, so that the subsequent surge model is not dependent on the structural parameters of the compression system any more, the surge model can be obtained by identifying the correction volume, the accuracy of a predicted result can be ensured by utilizing the surge model, the surge characteristic of the centrifugal compression system is truly reflected, and a reliable basis is provided for the design of an active surge control strategy of the centrifugal compression system.
Drawings
FIG. 1 is a schematic flow chart of the method of the present invention;
FIG. 2 is a schematic diagram of a centrifugal compression system for a fuel cell vehicle according to the present invention;
FIG. 3 is a comparison of the calculation results of the pneumatic performance analysis model of the centrifugal compressor with test data in the embodiment;
FIG. 4 is a graph showing the result of fitting the corrected volume to the rotational speed in the example;
FIG. 5a is a schematic diagram showing the comparison of the predicted result and the test result of the aerodynamic model of the surge process of the centrifugal compression system in the time domain at 30000r/min in the embodiment;
FIG. 5b is a schematic diagram showing the comparison between the predicted and experimental results of the aerodynamic model of the surge process of the centrifugal compression system in the frequency domain at 30000r/min in the embodiment;
FIG. 6a is a schematic diagram showing the comparison of the predicted results and the test results of the aerodynamic model of the surge process of the centrifugal compression system in the time domain at 65000r/min in the embodiment;
FIG. 6b is a graph showing the comparison of the predicted and experimental results in the frequency domain of the aerodynamic model of the surge process of the centrifugal compression system at 65000r/min in the example;
FIG. 7a is a schematic diagram showing the comparison of the predicted results and the test results of the aerodynamic model of the surge process of the centrifugal compression system in the time domain at 85000r/min in the embodiment;
FIG. 7b is a graph showing the comparison of the predicted and experimental results in the frequency domain of the aerodynamic model of the surge process of the centrifugal compression system at 85000r/min in the example;
FIG. 8 is a graph showing the comparison between the predicted value and the test value of the surge frequency of the centrifugal compression system under different rotational speed conditions in the embodiment.
Detailed Description
The invention will now be described in detail with reference to the drawings and specific examples.
Examples
As shown in fig. 1, a surge prediction method of a centrifugal compression system for a fuel cell vehicle includes the following steps:
s1, constructing a pneumatic performance analysis model of a centrifugal compressor for a fuel cell vehicle to obtain the pressure ratio characteristic of the centrifugal compressor, and particularly constructing the pneumatic performance analysis model of the centrifugal compressor to obtain the pressure ratio psi (m) c ω) and mass flow m c Relationship of rotational speed ω;
s2, based on a Moore-Greitzer surge model, combining the pressure ratio characteristics of the centrifugal compressor obtained in the step S1 to establish a surge aerodynamic model of the centrifugal compression system, and specifically:
firstly, establishing a Moore-Greitzer surge model according to the pressure ratio characteristic of the centrifugal compressor obtained in the step S1:
wherein p is p To compress the pressure of the system cavity, p 0 Is the external environmental pressure, V p To compress the volume of the system cavity, a 0 Is the sound velocity, k t Is the characteristic parameter of the electromagnetic valve, A is the area of the compressor, L c Is the length of the pipeline of the compression system;
and then correcting the Moore-Greitzer surge model (taking the influence of the outlet gas temperature of the centrifugal compressor on the sound velocity under different working conditions into consideration, and simultaneously introducing the correction volume of the centrifugal compression system into the Moore-Greitzer surge model to correct the Moore-Greitzer surge model) to obtain a centrifugal compression system surge aerodynamic model, wherein the influence of the outlet gas temperature of the centrifugal compressor on the sound velocity under different working conditions is specifically represented by the following formula:
wherein T is out For the outlet gas temperature of the centrifugal compressor, T in The temperature of inlet gas of the centrifugal compressor is gamma, and the specific heat ratio is gamma;
the correction volume of the centrifugal compression system is specifically as follows:
ΔV p ＝V p -L c ×A 1
wherein A is 1 To compress the system cavity pressure, deltaV p To correct the volume;
s3, obtaining pressure oscillation under the surge working condition of the centrifugal compressor through test measurement, and performing fast Fourier transform on the pressure oscillation to obtain surge frequency;
parameter identification is performed on the surge aerodynamic model established in the step S2 by using the surge frequency (in the embodiment, the correction volume in the surge aerodynamic model established in the step S2 is identified by using the surge frequency);
fitting the rotating speed and the identified parameters to obtain a surge model of the centrifugal compression system under the working condition of full rotating speed;
in practical application, the step S3 specifically includes the following steps:
s31, obtaining pressure oscillation of the centrifugal compressor in surge under different rotating speed working conditions through test measurement;
s32, performing fast Fourier transform on the measured pressure oscillation data to obtain corresponding surge frequency;
s33, identifying a correction volume in a surge aerodynamic model according to the surge frequency;
s34, based on the identified correction volume, further fitting by adopting a polynomial fitting mode to obtain a relation expression of the correction volume and the rotating speed, and substituting the relation expression into a surge aerodynamic model to obtain a surge model of the centrifugal compression system under the working condition of full rotating speed;
s4, inputting the rotation speed of the centrifugal compressor and the opening of the throttle valve into a surge model of the centrifugal compression system, outputting to obtain corresponding dynamic mass flow and gas pressure, and obtaining a surge prediction result.
By applying the technical scheme, the embodiment firstly needs to construct an aerodynamic model for obtaining the surge of the centrifugal compression system under the working condition of full rotation speed, and the model construction process comprises the following steps:
1. establishing a pneumatic performance analysis model of the centrifugal compressor for the fuel cell vehicle to calculate the pressure ratio characteristic through the rotating speed and the mass flow of the centrifugal compressor, namely, analyzing and modeling the centrifugal compressor to obtain the pressure ratio psi (m) c ω) and mass flow m c And the rotational speed omega;
2. based on a traditional Moore-Greitzer surge model, establishing an aerodynamic model of a surge process of a centrifugal compression system, correcting the surge model by considering the influence of outlet gas temperature on sound velocity under different working conditions of the centrifugal compressor, and simultaneously introducing a correction volume of the centrifugal compression system into the surge model for correction, wherein the method comprises the following steps of:
2.1, establishing an aerodynamic model of a surge process of a centrifugal compression system based on a traditional Moore-Greitzer surge model:
wherein p is p Representing the pressure of the compression system cavity, p 0 Represents the external environmental pressure, V p Representing the volume of a compression system cavity, a 0 Represents the sound velocity, k t Representing the characteristic parameters of the electromagnetic valve, A representing the compressor area, L c Representing the length of the compression system piping.
2.2, the influence of the outlet gas temperature of the centrifugal compressor under different working conditions on the sound velocity can be obtained through the formula (2);
wherein T is out Representing the outlet gas temperature of the centrifugal compressor.
The outlet gas temperature of the centrifugal compressor can be obtained by the method (3);
wherein T is in Represents the inlet gas temperature of the centrifugal compressor, and gamma represents the specific heat ratio
2.3, calculating the volume of the accommodating cavity of the centrifugal compression system through the formula (4);
V p ＝L c ×A 1 +ΔV p (4)
wherein A is 1 Representing the pressure of the compression system cavity, deltaV p Representing the corrected volume.
3. The method comprises the steps of testing and measuring pressure oscillation under a surge working condition of a centrifugal compressor, obtaining surge frequencies under different rotating speeds through fast Fourier transformation, identifying a correction volume in a surge model, and further fitting a relation between the correction volume and the rotating speed to obtain an aerodynamic model of the surge of the centrifugal compression system under a full-rotating-speed working condition, wherein the method comprises the following steps of:
3.1, performing fast Fourier transform on pressure pulsation measured by a test under different rotation speed working conditions when surging, obtaining surging frequency, and then identifying a correction volume in a surging model according to the surging frequency;
and 3.2, preliminarily judging the relation between the correction volume and the rotating speed, determining the times of a polynomial, and then utilizing polynomial fitting to determine the relation between the correction volume and the rotating speed, so as to establish an aerodynamic model of the surge of the centrifugal compression system under the working condition of full rotating speed.
The centrifugal compression system of the fuel cell used in this example is shown in fig. 2, and the basic parameters thereof are shown in table 1:
TABLE 1
| Variable(s) | (symbol) | Numerical value (Unit) |
| Ambient pressure of the environment | p 0 | 101.325(kPa) |
| Compressor area | A | 0.0222(m 2 ) |
| Compression system tubeTrack length | L c | 3.93(m) |
| Compression system conduit area | A 1 | 0.0015(m 2 ) |
The conventional dynamic modeling method of the surge process of the centrifugal compression system needs to consume a great deal of time to solve or is difficult to accurately predict the surge characteristic of the centrifugal compression system, and the problems can be better solved by adopting the method, and the specific process of the embodiment of the invention comprises the following steps:
and step 1, establishing a pneumatic performance analysis model of the centrifugal compressor for the fuel cell vehicle so as to calculate the pressure ratio characteristic through the rotating speed and the mass flow of the centrifugal compressor, wherein the pair of model results and test results are shown in figure 3.
And 2, correcting a traditional Moore-Greitzer surge model by considering the influence of outlet gas temperature on sound velocity under different working conditions of the centrifugal compressor, and simultaneously introducing a correction volume of a compression system into the model for correction.
1) An aerodynamic model of the surge process of the centrifugal compression system is established based on a traditional Moore-Greitzer surge model:
wherein p is p Representing the pressure of the compression system cavity, p 0 Represents the external environmental pressure, V p Representing the volume of a compression system cavity, a 0 Represents the sound velocity, k t Representing the characteristic parameters of the electromagnetic valve, A representing the compressor area, L c Representing the length of the compression system piping.
2) The influence of the outlet gas temperature of the centrifugal compressor under different working conditions on the sound velocity can be obtained through a formula (6);
wherein T is out Representing the outlet gas temperature of the centrifugal compressor.
The outlet gas temperature of the centrifugal compressor can be obtained by the method (7);
wherein T is in Represents the inlet gas temperature of the centrifugal compressor, and gamma represents the specific heat ratio
3) The volume of the cavity of the centrifugal compression system is obtained through a formula (8);
V p ＝L c ×A 1 +ΔV p (8)
wherein A is 1 Representing the pressure of the compression system cavity, deltaV p Representing the corrected volume.
Step 3, identifying the correction volume in the surge model based on the test data, and fitting the relation between the correction volume and the rotating speed
1) Performing fast Fourier transform on the pressure pulsation measured by the test under the working conditions of different rotating speeds in the surge process to obtain the surge frequency, and identifying the correction volume in the model according to the surge frequency, wherein the correction volume at each rotating speed is shown in figure 4;
2) The relation between the correction volume and the rotating speed is approximately a cubic curve relation through the trend of the correction volume changing along with the rotating speed, and a relation expression of the correction volume and the rotating speed is determined by using a cubic polynomial fitting. The results are shown in FIG. 4. And finally, substituting the relational expression into the formula (4) to establish an aerodynamic model of the surge of the centrifugal compression system under the working condition of full rotation speed.
And 4, predicting the surge characteristic under each rotating speed working condition through an aerodynamic model of the surge process of the centrifugal compression system, and comparing and verifying with test data, wherein as shown in figures 5a, 5b, 6a, 6b, 7a and 7b, the calculated result of the aerodynamic model of the surge process of the centrifugal compression system is better matched with the test result in both time domain and frequency domain, the feasibility and the accuracy of the dynamic modeling method are verified, and a foundation is provided for the design of an active surge control strategy of the centrifugal compression system for the fuel cell vehicle. Meanwhile, the method has high calculation efficiency, and can complete one-time simulation calculation only by a few seconds.
And 5, calculating the surge frequency at the full rotation speed through the aerodynamic model of the surge process of the centrifugal compression system, and comparing the surge frequency with a test result, wherein as shown in fig. 8, the method provided by the invention can accurately predict the surge characteristic, and the prediction error is within 2%.
The dynamic modeling method provided by the invention can predict the surge processes of various centrifugal compression systems and can provide a model foundation for the design of an active surge control strategy of the centrifugal compression system. In the embodiment, a centrifugal compression system for a certain fuel cell vehicle is taken as an example, and the specific implementation process of the method provided by the invention is described in detail; the embodiment predicts the surge process at each rotating speed, and the effectiveness of the invention is verified by comparing the surge process with the test result. In conclusion, the modeling method provided by the invention has low requirement on computational resources, can rapidly and accurately predict the surge process of the centrifugal compression system, further truly reflects the surge characteristic of the centrifugal compression system, provides an effective modeling method for researchers of the centrifugal compression system to rapidly and accurately predict the surge process, and can provide a reliable basis for designing an active surge control strategy of the centrifugal compression system through a model established by the method;
the modeling method provided by the invention does not need a large number of surge tests of the centrifugal compression system to identify parameters, and can avoid the operation of the centrifugal compressor under the surge working condition for a long time or frequently so as to ensure the safety of testers and equipment;
the design method provided by the invention is also applicable to centrifugal compressors with other purposes, and has universality.
Claims (4)
1. The surge prediction method of the centrifugal compression system for the fuel cell vehicle is characterized by comprising the following steps of:
s1, constructing a pneumatic performance analysis model of a centrifugal compressor for a fuel cell vehicle to obtain the pressure ratio characteristic of the centrifugal compressor;
s2, based on a Moore-Greitzer surge model, combining the pressure ratio characteristics of the centrifugal compressor obtained in the step S1 to establish a surge aerodynamic model of the centrifugal compression system;
s3, obtaining pressure oscillation under the surge working condition of the centrifugal compressor through test measurement, and performing fast Fourier transform on the pressure oscillation to obtain surge frequency;
carrying out parameter identification on the surge aerodynamic model established in the step S2 by utilizing the surge frequency;
fitting the rotating speed and the identified parameters to obtain a surge model of the centrifugal compression system under the working condition of full rotating speed;
s4, inputting the rotation speed of the centrifugal compressor and the opening of the throttle valve into a surge model of the centrifugal compression system, outputting to obtain corresponding dynamic mass flow and gas pressure, and obtaining a surge prediction result;
the step S2 specifically includes the following steps:
s21, establishing a Moore-Greitzer surge model according to the pressure ratio characteristic of the centrifugal compressor obtained in the step S1:
wherein p is p To compress the pressure of the system cavity, p 0 Is the external environmental pressure, V p To compress the volume of the system cavity, a 0 Is the sound velocity, k t Is the characteristic parameter of the electromagnetic valve, A is the area of the compressor, L c Is the length of the pipeline of the compression system;
s22, correcting the Moore-Greitzer surge model to obtain a surge aerodynamic model of the centrifugal compression system, and particularly, considering the influence of outlet gas temperature on sound velocity under different working conditions of the centrifugal compressor, and simultaneously introducing the correction volume of the centrifugal compression system into the Moore-Greitzer surge model to correct the Moore-Greitzer surge model;
the influence of the outlet gas temperature of the centrifugal compressor under different working conditions on the sound velocity is specifically represented by the following formula:
wherein T is out For the outlet gas temperature of the centrifugal compressor, T in The temperature of inlet gas of the centrifugal compressor is gamma, and the specific heat ratio is gamma;
the correction volume of the centrifugal compression system is specifically as follows:
ΔV p ＝V p -L c ×A 1
wherein A is 1 To compress the system cavity pressure, deltaV p To correct the volume;
the step S3 specifically comprises the following steps:
s31, obtaining pressure oscillation of the centrifugal compressor in surge under different rotating speed working conditions through test measurement;
s32, performing fast Fourier transform on the measured pressure oscillation data to obtain corresponding surge frequency;
s33, identifying a correction volume in a surge aerodynamic model according to the surge frequency;
s34, based on the identified correction volume, further fitting to obtain a relation expression of the correction volume and the rotating speed, and substituting the relation expression into a surge aerodynamic model to obtain the surge model of the centrifugal compression system under the working condition of full rotating speed.
2. The method for predicting surge of a centrifugal compression system for a fuel cell vehicle according to claim 1, wherein the step S1 is specifically to construct a pneumatic performance analysis model of a centrifugal compressor to obtain a centrifugal compressor pressureRatio psi (m) c ω) and mass flow m c And the rotational speed omega.
3. The method for predicting surge of a centrifugal compression system for a fuel cell vehicle according to claim 1, wherein the step S3 specifically uses the surge frequency to identify the corrected volume in the surge aerodynamic model established in the step S2.
4. The method for predicting surge of a centrifugal compression system for a fuel cell vehicle according to claim 1, wherein the step S34 is specifically to fit a polynomial fitting method to obtain a relation expression of correction volume and rotation speed.
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Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02102397A (en) * | 1988-10-11 | 1990-04-13 | Mitsubishi Heavy Ind Ltd | Method of controlling surge in centrifugal or axial compressor |
| US5984625A (en) * | 1996-10-15 | 1999-11-16 | California Institute Of Technology | Actuator bandwidth and rate limit reduction for control of compressor rotating stall |
| CN110848166A (en) * | 2019-11-13 | 2020-02-28 | 西北工业大学 | Axial flow compressor surge frequency prediction method |
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Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02102397A (en) * | 1988-10-11 | 1990-04-13 | Mitsubishi Heavy Ind Ltd | Method of controlling surge in centrifugal or axial compressor |
| US5984625A (en) * | 1996-10-15 | 1999-11-16 | California Institute Of Technology | Actuator bandwidth and rate limit reduction for control of compressor rotating stall |
| CN110848166A (en) * | 2019-11-13 | 2020-02-28 | 西北工业大学 | Axial flow compressor surge frequency prediction method |
Non-Patent Citations (1)
| Title |
|---|
| 压气机动态模型的建立及喘振过程分析;王伟才;王银燕;;热能动力工程(第02期);全文 * |
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