CN113688510A - Surging 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; establishing a surge aerodynamic model of the centrifugal compression system based on the Moore-Greitzer surge model and in combination with the pressure ratio characteristic of the centrifugal compressor; obtaining pressure oscillation under the surge 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 a surge aerodynamic model by utilizing 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 rotating speed and the opening degree of the throttle valve of the centrifugal compressor into a surge model of the centrifugal compression system, and outputting to obtain a corresponding surge prediction result. Compared with the prior art, the method can quickly and accurately predict the surge characteristic 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 commercial popularization of fuel cell automobiles, the fuel cell industry has been rapidly developed. An air compressor is a key component of a fuel cell system and 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 an air compressor for a fuel cell vehicle, and therefore, most of the mainstream air-assisted systems for the vehicle fuel cell are the centrifugal compressor. However, the centrifugal compressor is easy to surge under the working condition of low mass flow, even causes system damage in serious conditions, and the stable working range of the centrifugal compressor can be greatly influenced by the surge. The centrifugal compressor cannot work under a surge condition for a long time or frequently, and if the surge characteristic is researched through a large number of tests, dangers are inevitably brought to testers and equipment. In order to study surge characteristics and design an active surge control strategy, it is necessary to predict the surge process of the centrifugal compression system for a fuel cell vehicle.
Chinese patent CN107924425A proposes a method for predicting surge in an air compressor, which can predict the surge boundary of the air 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 establish a Computational Fluid Dynamics (CFD) simulation model of the air compressor for numerical simulation, has extremely high requirements on computational resources, and is difficult to be used as a model basis for active surge control strategy design. Chinese patent CN110848166A proposes a method for predicting the surge frequency of an axial flow compressor, which avoids experimental measurement and is mainly aimed at the axial flow compressor, the prediction result of the method depends greatly on the structural parameters of the compression system, and the early determination of the parameters is difficult, so that the method is difficult to accurately predict the surge characteristic and cannot be used as the model basis for the design of the active surge control strategy of the centrifugal compression system.
Disclosure of Invention
The present invention is directed to overcome the above-mentioned drawbacks of the prior art, and an object of the present invention is to provide a method for predicting surge of a centrifugal compression system for a fuel cell vehicle, so as to rapidly and accurately predict surge characteristics of the centrifugal compression system without relying on a large number of surge tests of the centrifugal compressor.
The purpose of the invention can be realized by the following technical scheme: a surge prediction method of a centrifugal compression system for a fuel cell vehicle includes the steps of:
s1, 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;
s2, establishing a surge aerodynamic model of the centrifugal compression system based on the Moore-Greitzer surge model by combining the pressure ratio characteristics of the centrifugal compressor obtained in the step S1;
s3, obtaining pressure oscillation under the surge condition of the centrifugal compressor through test measurement, and carrying out fast Fourier transform on the pressure oscillation to obtain surge frequency;
performing parameter identification on the surge aerodynamic model established in the step S2 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;
and S4, inputting the rotating speed and the throttle opening of the centrifugal compressor into a surge model of the centrifugal compression system, and outputting to obtain corresponding dynamic mass flow and gas pressure to obtain a surge prediction result.
Further, the step S1 is specifically to construct an analysis model of the pneumatic performance of the centrifugal compressor to obtain a pressure ratio ψ (m) of the centrifugal compressorcω) and mass flow mcAnd the rotational speed ω.
Further, the step S2 specifically includes the following steps:
s21, establishing a Moore-Greitzer surge model according to the pressure ratio characteristics of the centrifugal compressor obtained in the step S1;
and S22, correcting the Moore-Greitzer surge model to obtain a surge aerodynamic model of the centrifugal compression system.
Further, the step S22 is to take into account the influence of the outlet gas temperature of the centrifugal compressor under different conditions on the sound velocity, and introduce 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 specifically includes:
wherein p ispFor compressing the system chamber pressure, p0At the pressure of the external environment, VpFor compressing the volume of the chamber of the system, a0Is the speed of sound, ktIs the characteristic parameter of the electromagnetic valve, A is the compressor area, LcTo compress the system pipe length.
Further, the influence of the outlet gas temperature of the centrifugal compressor under different working conditions on the sound velocity is embodied by the following formula:
wherein, ToutIs the outlet gas temperature, T, of the centrifugal compressorinγ is the specific heat ratio, which is the inlet gas temperature of the centrifugal compressor.
Further, the corrected volume of the centrifugal compression system is specifically:
ΔVp＝Vp-Lc×A1
wherein A is1For compressing the system chamber pressure, Δ VpTo correct the volume.
Further, the step S3 is to identify the corrected volume in the surge aerodynamic model established in the step S2 by using the surge frequency.
Further, the step S3 specifically includes the following steps:
s31, obtaining pressure oscillation of the centrifugal compressor during surging 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 the surge aerodynamic model according to the surge frequency;
and S34, further fitting to obtain a relational expression of the corrected volume and the rotating speed based on the identified corrected volume, and substituting the relational expression into a surge aerodynamic model to obtain a surge model of the centrifugal compression system under the full-rotating-speed working condition.
Further, in the step S34, a polynomial fitting manner is specifically adopted to fit to obtain a relational expression between the corrected volume and the rotation speed.
Compared with the prior art, the invention has the following advantages:
firstly, the invention obtains the pressure ratio characteristic of the centrifugal compressor by establishing a pneumatic performance analytical model of the centrifugal compressor, combines the traditional Moore-Greitzer surge model and corrects the surge aerodynamic model, only needs to test and measure the pressure oscillation of the centrifugal compressor, can identify the parameters of the surge aerodynamic model, obtains the fitting relation between the parameters and the rotating speed by combining the identification, and further obtains the surge model of the centrifugal compression system under the working condition of the full rotating speed, thereby greatly reducing the requirement on computing resources, and simultaneously can quickly establish an accurate surge model without carrying out a large number of surge tests of the centrifugal compression system, thereby ensuring that the surge process of the centrifugal compression system can be quickly and accurately predicted subsequently.
Secondly, the pressure oscillation of the centrifugal compressor under the surging working conditions of different rotating speeds 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, the centrifugal compressor can be prevented from running under the surging working conditions for a long time or frequently, and the safety of testing personnel and equipment is ensured.
Thirdly, the influence of outlet gas temperature of the centrifugal compressor under different working conditions on sound velocity is considered, meanwhile, the correction volume of the centrifugal compression system is introduced into the surge model, and the Moore-Greitzer surge model is corrected, so that the surge aerodynamic model of the centrifugal compression system is obtained, the subsequent surge model does not depend on structural parameters of the compression system any more, the surge model can be obtained only by identifying the correction volume, the accuracy of a prediction result can be guaranteed 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 diagram of the process of the present invention;
FIG. 2 is a schematic view 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 in the embodiment with the test data;
FIG. 4 is a fitting result of the corrected volume and the rotation speed in the embodiment;
FIG. 5a is a schematic diagram showing the comparison of the prediction result and the test result of the aerodynamic model of the surging process of the centrifugal compression system at the rotating speed of 30000r/min in the time domain in the embodiment;
FIG. 5b is a schematic diagram showing the comparison of the prediction result and the test result of the aerodynamic model of the surging process of the centrifugal compression system at the rotating speed of 30000r/min in the frequency domain in the embodiment;
FIG. 6a is a schematic diagram of the prediction result of the aerodynamic model of the surging process of the centrifugal compression system in the time domain and the test result when the rotating speed is 65000r/min in the embodiment;
FIG. 6b is a schematic diagram showing the comparison of the prediction result and the test result of the aerodynamic model of the surging process of the centrifugal compression system in the frequency domain when the rotating speed is 65000r/min in the embodiment;
FIG. 7a is a schematic diagram of the prediction result of the aerodynamic model of the surging process of the centrifugal compression system in the time domain when the rotating speed is 85000r/min and the test result in comparison in the embodiment;
FIG. 7b is a schematic diagram showing the comparison of the prediction result and the test result of the aerodynamic model of the surging process of the centrifugal compression system at the rotating speed of 85000r/min in the frequency domain in the embodiment;
FIG. 8 is a diagram illustrating comparison between a predicted value and a test value of a model of a surge frequency of a centrifugal compression system under different rotation speed conditions in the embodiment.
Detailed Description
The invention is described in detail below with reference to the figures and specific embodiments.
Examples
As shown in fig. 1, a surge prediction method of a centrifugal compression system for a fuel cell vehicle includes the steps of:
s1, constructing a centrifugal compressor pneumatic performance analysis model for the fuel cell vehicle to obtain the pressure ratio characteristic of the centrifugal compressor, specifically, constructing the centrifugal compressor pneumatic performance analysis model to obtain the pressure ratio psi (m) of the centrifugal compressorcω) and mass flow mcThe relation of the rotation speed omega;
s2, establishing a surge aerodynamic model of the centrifugal compression system based on the Moore-Greitzer surge model and by combining the pressure ratio characteristic of the centrifugal compressor obtained in the step S1, 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 ispFor compressing the system chamber pressure, p0At the pressure of the external environment, VpFor compressing the volume of the chamber of the system, a0Is the speed of sound, ktIs the characteristic parameter of the electromagnetic valve, A is the compressor area, LcTo compress system pipe length;
and then correcting the Moore-Greitzer surge model (considering the influence of the outlet gas temperature of the centrifugal compressor under different working conditions on the sound velocity, introducing the correction volume of the centrifugal compression system into the Moore-Greitzer surge model at the same time, and correcting the Moore-Greitzer surge model) to obtain a surge aerodynamic model of the centrifugal compression system, wherein the influence of the outlet gas temperature of the centrifugal compressor under different working conditions on the sound velocity is embodied by the following formula:
in the formula, ToutIs the outlet gas temperature, T, of the centrifugal compressorinIs the inlet gas temperature of the centrifugal compressor, and gamma is the specific heat ratio;
the corrected volume of the centrifugal compression system is specifically:
ΔVp＝Vp-Lc×A1
in the formula, A1For compressing the system chamber pressure, Δ VpTo correct the volume;
s3, obtaining pressure oscillation under the surge condition of the centrifugal compressor through test measurement, and carrying out fast Fourier transform on the pressure oscillation to obtain surge frequency;
identifying parameters of the surge aerodynamic model created in step S2 using the surge frequency (in the present embodiment, identifying the correction volume in the surge aerodynamic model created in step S2 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 applications, step S3 specifically includes the following steps:
s31, obtaining pressure oscillation of the centrifugal compressor during surging 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 the surge aerodynamic model according to the surge frequency;
s34, further fitting to obtain a relational expression of the correction volume and the rotating speed by adopting a polynomial fitting mode based on the identified correction volume, and substituting the relational expression into a surge aerodynamic model to obtain a surge model of the centrifugal compression system under the full-rotating-speed working condition;
and S4, inputting the rotating speed and the throttle opening of the centrifugal compressor into a surge model of the centrifugal compression system, and outputting to obtain corresponding dynamic mass flow and gas pressure to obtain a surge prediction result.
According to the technical scheme, firstly, an aerodynamic model of the surge of the centrifugal compression system under the full-rotating-speed working condition needs to be constructed, and the construction process of the model comprises the following steps:
firstly, establishing a pneumatic performance analysis model of a centrifugal compressor for a fuel cell vehicle, calculating pressure ratio characteristics through the rotating speed and mass flow of the centrifugal compressor, namely analyzing and modeling the centrifugal compressor to obtain the pressure ratio psi (m) of the centrifugal compressorcω) and mass flow mcAnd the rotational speed ω;
secondly, based on the traditional Moore-Greitzer surge model, an aerodynamic model of the surge process of the centrifugal compression system is established, the influence of the outlet gas temperature of the centrifugal compressor under different working conditions on the sound velocity is considered to correct the surge model, and meanwhile, the correction volume of the centrifugal compression system is introduced into the surge model to correct, and the method is specific:
2.1, establishing an aerodynamic model of the surge process of the centrifugal compression system based on the traditional Moore-Greitzer surge model:
wherein p ispRepresenting the compression system chamber pressure, p0Indicating the ambient pressure, VpRepresenting the volume of the compression system chamber, a0Representing the speed of sound, ktIndicating the characteristic parameters of the solenoid valve, A the area of the compressor, LcRepresenting the compression system pipe length.
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 isoutIndicating the outlet gas temperature of the centrifugal compressor.
The outlet gas temperature of the centrifugal compressor can be obtained by the formula (3);
wherein T isinDenotes the inlet gas temperature of the centrifugal compressor, gamma denotes the specific heat ratio
2.3, solving the volume of the containing cavity of the centrifugal compression system by the formula (4);
Vp＝Lc×A1+ΔVp (4)
wherein A is1Representing compression system chamber pressure, Δ VpThe corrected volume is represented.
Pressure oscillation under the surge working condition of the centrifugal compressor is measured in an experiment, surge frequency under different rotating speeds is obtained through fast Fourier transform, the correction volume in a surge model is identified, then the relation between the correction volume and the rotating speed is fitted, and an aerodynamic model of the surge of the centrifugal compression system under the working condition of full rotating speed is obtained, specifically:
3.1, performing fast Fourier transform on pressure pulsation under different rotation speed working conditions, which is measured by tests, during surging to obtain surging frequency, and then identifying the correction volume in a surging model according to the surging frequency;
and 3.2, preliminarily judging the relation between the corrected volume and the rotating speed, determining the times of a polynomial, and determining the relation between the corrected volume and the rotating speed by utilizing polynomial fitting so as to establish an aerodynamic model of the surge of the centrifugal compression system under the full-rotating-speed working condition.
The fuel cell centrifugal compression system used in this example is shown in fig. 2, and its basic parameters are shown in table 1:
TABLE 1
| Variables of | (symbol) | Numerical value (Unit) |
| Ambient pressure | p0 | 101.325(kPa) |
| Area of compressor | A | 0.0222(m2) |
| Compression system pipe length | Lc | 3.93(m) |
| Compression system pipe area | A1 | 0.0015(m2) |
The conventional dynamic modeling method for the surge process of the centrifugal compression system needs to consume a large amount of time to solve or is difficult to accurately predict the surge characteristic of the centrifugal compression system, the problems can be well solved by adopting the method, and the specific process of applying the method disclosed by the embodiment of the invention is as follows:
And 2, correcting the traditional Moore-Greitzer surge model by considering the influence of the outlet gas temperature of the centrifugal compressor under different working conditions on the sound velocity, and introducing the correction volume of the compression system into the model for correction.
1) An aerodynamic model of a surge process of a centrifugal compression system is established on the basis of a traditional Moore-Greitzer surge model:
wherein p ispRepresenting the compression system chamber pressure, p0Indicating the ambient pressure, VpRepresenting the volume of the compression system chamber, a0Representing the speed of sound, ktIndicating the characteristic parameters of the solenoid valve, A the area of the compressor, LcRepresenting the compression system pipe length.
2) The influence of the outlet gas temperature of the centrifugal compressor under different working conditions on the sound velocity can be solved through the formula (6);
wherein T isoutIndicating the outlet gas temperature of the centrifugal compressor.
The outlet gas temperature of the centrifugal compressor can be obtained by the formula (7);
wherein T isinDenotes the inlet gas temperature of the centrifugal compressor, gamma denotes the specific heat ratio
3) The volume of the containing cavity of the centrifugal compression system is obtained by the formula (8);
Vp＝Lc×A1+ΔVp (8)
wherein A is1Representing compression system chamber pressure, Δ VpThe corrected volume is represented.
1) Performing fast Fourier transform on pressure pulsation of the pressure pulsation under different rotating speed working conditions, which is measured in a test, to obtain a surge frequency, and then identifying a correction volume in the model according to the surge frequency, wherein the correction volume at each rotating speed is shown in FIG. 4;
2) the approximate cubic curve relationship between the corrected volume and the rotating speed can be seen through the trend of the corrected volume changing along with the rotating speed, and the relational expression of the corrected volume and the rotating speed is determined by utilizing cubic polynomial fitting. The results are shown in FIG. 4. And finally, the relational expression is substituted into the formula (4), and an aerodynamic model of the surge of the centrifugal compression system under the full-rotating-speed working condition can be established.
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 the surge characteristic with test data, as shown in the figures 5a, 5b, 6a, 6b, 7a and 7b, wherein the result obtained by calculation of the aerodynamic model of the surge process of the centrifugal compression system is better matched with the test result in a time domain and a frequency domain, the feasibility and the accuracy of the dynamic modeling method are verified, and a basis 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 in a few seconds.
And 5, calculating the surge frequency under the full rotating speed through the aerodynamic model of the surge process of the centrifugal compression system, and comparing the calculated surge frequency with the test result, as shown in figure 8, wherein the method can accurately predict the surge characteristic, and the prediction error is within 2 percent.
The dynamic modeling method provided by the invention can predict the surge process of various centrifugal compression systems and can provide a model basis for the design of an active surge control strategy of the centrifugal compression system. The present embodiment takes a centrifugal compression system for a fuel cell vehicle as an example, and details the specific implementation process of the method provided by the present invention; the embodiment predicts the surging process at each rotating speed and compares the surging process with the test result to verify the effectiveness of the invention. In conclusion, the modeling method provided by the invention has low requirement on computing resources, can quickly 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 a centrifugal compression system researcher to quickly and accurately predict the surge process, and can provide a reliable basis for the design of an active surge control strategy of the centrifugal compression system;
the modeling method provided by the invention does not need a large amount of surge tests of the centrifugal compression system to identify parameters, and can avoid the centrifugal compressor from running under a surge working condition for a long time or frequently so as to ensure the safety of testing personnel and equipment;
the design method provided by the invention is also suitable for centrifugal compressors of other purposes, and has universality.
Claims (10)
1. A surge prediction method of a centrifugal compression system for a fuel cell vehicle is characterized by comprising the following steps:
s1, 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;
s2, establishing a surge aerodynamic model of the centrifugal compression system based on the Moore-Greitzer surge model by combining the pressure ratio characteristics of the centrifugal compressor obtained in the step S1;
s3, obtaining pressure oscillation under the surge condition of the centrifugal compressor through test measurement, and carrying out fast Fourier transform on the pressure oscillation to obtain surge frequency;
performing parameter identification on the surge aerodynamic model established in the step S2 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;
and S4, inputting the rotating speed and the throttle opening of the centrifugal compressor into a surge model of the centrifugal compression system, and outputting to obtain corresponding dynamic mass flow and gas pressure to obtain a surge prediction result.
2. The method of claim 1The surge prediction method of the centrifugal compression system for the fuel cell vehicle is characterized in that the step S1 is specifically to construct a pneumatic performance analysis model of the centrifugal compressor so as to obtain the pressure ratio psi (m) of the centrifugal compressorcω) and mass flow mcAnd the rotational speed ω.
3. The surge prediction method of a centrifugal compression system for a fuel cell vehicle as claimed in claim 2, wherein the step S2 specifically comprises the steps of:
s21, establishing a Moore-Greitzer surge model according to the pressure ratio characteristics of the centrifugal compressor obtained in the step S1;
and S22, correcting the Moore-Greitzer surge model to obtain a surge aerodynamic model of the centrifugal compression system.
4. The surge prediction method for the centrifugal compression system of the fuel cell vehicle as claimed in claim 3, wherein the step S22 is implemented by taking into account the influence of the outlet gas temperature of the centrifugal compressor under different conditions on the sound velocity and introducing the correction volume of the centrifugal compression system into the Moore-Greizer surge model to correct the Moore-Greizer surge model.
5. The surge prediction method of the centrifugal compression system for the fuel cell vehicle as claimed in claim 4, wherein the Moore-Greitzer surge model established in the step S21 is specifically:
wherein p ispFor compressing the system chamber pressure, p0At the pressure of the external environment, VpFor compressing the volume of the chamber of the system, a0Is the speed of sound, ktIs the characteristic parameter of the electromagnetic valve, A is the compressor area, LcTo compress the system pipe length.
6. The surge prediction method of the centrifugal compression system for the fuel cell vehicle as claimed in claim 5, wherein the influence of the outlet gas temperature of the centrifugal compressor under different working conditions on the sound velocity is embodied by the following formula:
wherein, ToutIs the outlet gas temperature, T, of the centrifugal compressorinγ is the specific heat ratio, which is the inlet gas temperature of the centrifugal compressor.
7. The surge prediction method of a centrifugal compression system for a fuel cell vehicle as claimed in claim 5, wherein the correction volume of the centrifugal compression system is specifically:
ΔVp＝Vp-Lc×A1
wherein A is1For compressing the system chamber pressure, Δ VpTo correct the volume.
8. The surge prediction method for the centrifugal compression system of the fuel cell vehicle as claimed in claim 4, wherein the step S3 is to identify the corrected volume in the surge aerodynamic model established in the step S2 by using the surge frequency.
9. The surge prediction method of a centrifugal compression system for a fuel cell vehicle as claimed in claim 8, wherein the step S3 specifically comprises the steps of:
s31, obtaining pressure oscillation of the centrifugal compressor during surging 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 the surge aerodynamic model according to the surge frequency;
and S34, further fitting to obtain a relational expression of the corrected volume and the rotating speed based on the identified corrected volume, and substituting the relational expression into a surge aerodynamic model to obtain a surge model of the centrifugal compression system under the full-rotating-speed working condition.
10. The surge prediction method of a centrifugal compression system for a fuel cell vehicle as claimed in claim 9, wherein the step S34 is to fit a polynomial fitting manner to obtain the relational expression of the corrected volume and the rotation speed.
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| CN115356096A (en) * | 2022-08-18 | 2022-11-18 | 西安交通大学 | System and method for researching surge characteristic of compressor pipe network system |
| CN117851765A (en) * | 2024-03-07 | 2024-04-09 | 中国空气动力研究与发展中心高速空气动力研究所 | Low-temperature axial flow compressor performance parameter normalization method considering real gas effect |
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Cited By (4)
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| CN115356096A (en) * | 2022-08-18 | 2022-11-18 | 西安交通大学 | System and method for researching surge characteristic of compressor pipe network system |
| CN115356096B (en) * | 2022-08-18 | 2024-05-14 | 西安交通大学 | System and method for researching surge characteristics of compressor pipe network system |
| CN117851765A (en) * | 2024-03-07 | 2024-04-09 | 中国空气动力研究与发展中心高速空气动力研究所 | Low-temperature axial flow compressor performance parameter normalization method considering real gas effect |
| CN117851765B (en) * | 2024-03-07 | 2024-05-10 | 中国空气动力研究与发展中心高速空气动力研究所 | Low-temperature axial flow compressor performance parameter normalization method considering real gas effect |
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| CN113688510B (en) | 2024-02-27 |
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