CN111832189B - Centrifugal vapor compressor model selection method - Google Patents
Centrifugal vapor compressor model selection method Download PDFInfo
- Publication number
- CN111832189B CN111832189B CN202010725814.7A CN202010725814A CN111832189B CN 111832189 B CN111832189 B CN 111832189B CN 202010725814 A CN202010725814 A CN 202010725814A CN 111832189 B CN111832189 B CN 111832189B
- Authority
- CN
- China
- Prior art keywords
- exhaust
- vapor compressor
- intake
- centrifugal vapor
- centrifugal
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/17—Mechanical parametric or variational design
Abstract
The invention belongs to the technical field of vapor compressors, and particularly discloses a centrifugal vapor compressor model selection method, which comprises the following steps: s1, calculating the exhaust pressure and the total exhaust enthalpy of the centrifugal vapor compressor under different flow rates; s2, inquiring the following performance parameters at the given air inlet temperature: the intake density, the intake entropy, the intake total enthalpy, the exhaust isentropic density, the exhaust isentropic total enthalpy and the exhaust density; s3, carrying out dimensionless transformation on the performance parameters in the S2 to obtain a dimensionless performance curve of the centrifugal vapor compressor; s4, determining the corresponding rotating speed under the new given operating condition; s5, obtaining the accurate rotating speed under the new given operating condition; and outputting the gas flow, the exhaust pressure, the variable efficiency and the pneumatic power of the gas inlet at an accurate rotating speed, and drawing a performance curve. The method can solve the problems of long time consumption and large occupied computer resources of the existing type selection method.
Description
Technical Field
The invention belongs to the technical field of vapor compressors, and particularly relates to a centrifugal vapor compressor model selection method.
Background
The steam compressor is a key device for improving the temperature and the pressure of steam generated by a heat recovery system through the compression action of the steam, and has the function of pressurizing and heating low-pressure (or low-temperature) steam to meet the temperature and pressure requirements required by the process or engineering. Vapor compressors generally include roots-type compressors (positive displacement), centrifugal compressors (speed), and the like.
At present, when a centrifugal steam compressor is used for model selection, a detailed performance type spectrum needs to be provided, such as fig. 1, 2 and 3, which include performance type spectrums of flow-pressure ratio, flow-efficiency and flow-power, and certain numerical calculation is assisted, so that more accurate unit operation parameters can be obtained, and the model of a unit is determined. The performance type spectrum is adopted to determine the type of the unit, and the following defects exist: firstly, a large amount of time and computer resources are consumed for carrying out numerical calculation on a variable-speed performance type spectrum; secondly, after the temperature rise of the unit is changed, if the rotating speed interval on the performance type spectrum is large, the necessary parameters such as accurate efficiency, boosting, power and the like are difficult to obtain by referring to the variable rotating speed performance type spectrum; if the interval of the rotating speed is smaller, more time and resources are consumed to carry out numerical calculation; when the temperature of the inlet of the centrifugal steam compressor changes, the operating speed of the unit and the performance curve of the computer unit need to be determined again, and whether the working flow of the unit is in a high-efficiency area or not and whether the working flow has a wider adjusting range or not can be accurately judged.
Disclosure of Invention
The invention aims to provide a centrifugal vapor compressor model selection method, which aims to solve the problems of long time consumption and more occupied computer resources in the existing model selection method.
In order to achieve the purpose, the technical scheme of the invention is as follows: a centrifugal vapor compressor sizing method comprising the steps of:
s1, calculating the exhaust pressure and the total exhaust enthalpy of the centrifugal vapor compressor under different flow rates according to the performance parameters of the centrifugal vapor compressor;
s2, inquiring the following performance parameters at the given air inlet temperature: the intake density, the intake entropy, the intake total enthalpy, the exhaust isentropic density, the exhaust isentropic total enthalpy and the exhaust density;
s3, carrying out non-dimensionalization on the performance parameters in the S2 to obtain a non-dimensionalized performance curve of the centrifugal steam compressor, wherein the non-dimensionalized performance curve comprises an energy head coefficient-flow coefficient curve and a polytropic efficiency-flow coefficient curve;
s4, determining the corresponding rotating speed under the new given operating condition; the new given operation conditions comprise an air inlet saturation temperature, a saturation temperature rise and a required flow; calculating the pressure ratio and the polytropic efficiency of the centrifugal steam compressor at the corresponding rotating speed according to the required flow in the newly given operating condition;
s5, comparing the pressure ratio calculated in S4 with the required pressure ratio, and adjusting the rotating speed to meet the requirement of the required pressure ratio, so as to obtain the accurate rotating speed under the newly given operating condition; calculating to obtain the exhaust pressure, the total exhaust enthalpy, the intake density, the intake entropy, the total intake enthalpy, the isentropic exhaust density, the total isentropic exhaust enthalpy and the exhaust density of the centrifugal vapor compressor at an accurate rotating speed, thereby obtaining the pneumatic power of the centrifugal vapor compressor; and outputting the gas flow, the exhaust pressure, the variable efficiency and the pneumatic power of the gas inlet at an accurate rotating speed, and drawing a performance curve.
The different working conditions of the centrifugal vapor compressor are mainly represented by the air inlet saturation temperature and the saturation temperature rise, so that after the air inlet saturation temperature, the saturation temperature rise and the required flow are given, whether a unit under the original design parameters (usually, the original design parameters are different from the given parameters) of the centrifugal vapor compressor can be selected, and the running rotating speed under the new given parameters needs to be determined to ensure that the centrifugal vapor compressor unit meets the requirement of acting under the required flow at the rotating speed.
Further, in step S2, the intake density, the intake entropy and the intake total enthalpy at a given intake temperature are queried by the water vapor physical property parameter software; searching out the isentropic density and the isentropic total enthalpy of the exhaust according to the exhaust pressure and the intake entropy; and (5) searching the exhaust density according to the exhaust pressure and the total enthalpy of the exhaust.
Further, in step S3, the flow coefficient is expressed as φ*，
The polytropic efficiency is expressed as etap *，
The head coefficient is denoted by psi*，
Wherein n represents the polytropic process exponent,
f is the coefficient of the polytropic pressure head,
nsin order to be an index of the isentropic process,
wherein QinRepresenting the gas flow rate of the inlet port, pinDenotes the gas density of the gas inlet, D2Denotes the diameter at the impeller exit, pinFor intake pressure, poutIs the discharge pressure, vinIs the specific volume of intake air, voutIs specific volume of exhaust gas, vout,sIs the specific volume of exhaust gas in the isentropic process, hinIs the total enthalpy of intake, houtIs the total enthalpy of exhaust, hout,sThe total enthalpy of exhaust in the isentropic process, and N is the rotating speed.
Further, in step S4, the aerodynamic power is represented by P, and P is Qin*(hout-hin)。
Further, in step S4, according to the fact that the Mach number of the machine under the new given operation condition is equal to the Mach number of the machine under the original design parameter of the centrifugal vapor compressor, the corresponding rotation speed under the new given operation condition can be obtained,
M＝M*where M denotes the Mach number of the machine under the newly given operating conditions, M*Representing the machine Mach number u, at the original design parameters of the centrifugal vapor compressor2Indicating the peripheral speed at the impeller outlet at the corresponding rotational speed, u2 *For the peripheral speed at the impeller exit at the original design parameters of the centrifugal vapor compressor,
ainfor the inlet sound velocity at the newly given operating conditions, ain *Is the inlet sound velocity at the original design parameters of the centrifugal vapor compressor.
Further, in step S4, the head coefficient ψ and the polytropic efficiency η at the corresponding rotation speedpCentrifugation at the original design parameters of a centrifugal vapor compressorThe energy head coefficient and the polytropic efficiency of the vapor compressor respectively have corresponding equivalent relations, namely psi ═ alpha ^ psi*，
Wherein psi*Representing the energy head coefficient, η, at the original design parameters of a centrifugal vapor compressorp *Expressing the polytropic efficiency of the centrifugal vapor compressor under the original design parameters, alpha and beta are empirical coefficients related to the inlet air temperature.
The beneficial effects of this technical scheme lie in: when a user requires temperature rise change and air inlet temperature is not changed, the accurate operation rotating speed is not required to be determined through trial numerical calculation, the rotating speed can be directly input to check the output pressure, the operation rotating speed of the centrifugal steam compressor can be accurately determined, and time cost can be greatly saved. When the user requires the air inlet temperature to change, the accurate running rotating speed is not required to be determined through trial numerical calculation, and meanwhile, the performance curve under the rotating speed is not required to be obtained through numerical calculation to judge whether the working condition is in a high-efficiency area or not and whether the working condition has a wider adjusting range or not; only need input corresponding inlet air temperature, adjust the rotational speed, through looking over and contrasting the exhaust pressure, can output corresponding performance curve, can accurately judge whether this operating mode is in the high efficiency region, whether have the wide control range.
Drawings
FIG. 1 is a graph of a flow-to-pressure ratio profile of the background art;
FIG. 2 is a graph of flow-efficiency performance profiles of the background art;
FIG. 3 is a graph of flow versus power performance in the background art;
FIG. 4 is a flow diagram of a centrifugal vapor compressor sizing method of the present invention.
Detailed Description
The following is further detailed by way of specific embodiments:
the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The examples are substantially as shown in figures 1 to 4 of the accompanying drawings: a centrifugal vapor compressor sizing method comprising the steps of:
s1, calculating the exhaust pressure and the total exhaust enthalpy of the centrifugal vapor compressor under different flow rates according to the performance parameters of the centrifugal vapor compressor;
s2, inquiring the following performance parameters at the given air inlet temperature: the intake density, the intake entropy, the intake total enthalpy, the exhaust isentropic density, the exhaust isentropic total enthalpy and the exhaust density;
s3, carrying out non-dimensionalization on the performance parameters in the S2 to obtain a non-dimensionalized performance curve of the centrifugal steam compressor, wherein the non-dimensionalized performance curve comprises an energy head coefficient-flow coefficient curve and a polytropic efficiency-flow coefficient curve;
s4, determining the corresponding rotating speed under the new given operating condition; the new given operation conditions comprise an air inlet saturation temperature, a saturation temperature rise and a required flow; calculating the pressure ratio and the polytropic efficiency of the centrifugal steam compressor at the corresponding rotating speed according to the required flow in the newly given operating condition;
the different working conditions of the centrifugal vapor compressor are mainly represented by the air inlet saturation temperature and the saturation temperature rise, so that after the air inlet saturation temperature, the saturation temperature rise and the required flow are given, whether a unit under the original design parameters (usually, the original design parameters are different from the given parameters) of the centrifugal vapor compressor can be selected, and the running rotating speed under the new given parameters needs to be determined to ensure that the centrifugal vapor compressor unit meets the requirement of acting under the required flow at the rotating speed.
S5, comparing the pressure ratio calculated in S4 with the required pressure ratio, and adjusting the rotating speed to meet the requirement of the required pressure ratio, so as to obtain the accurate rotating speed under the newly given operating condition; calculating to obtain the exhaust pressure, the total exhaust enthalpy, the intake density, the intake entropy, the total intake enthalpy, the isentropic density of exhaust and the total isentropic enthalpy of exhaust of the centrifugal vapor compressor at the accurate rotating speedAnd a discharge density, thereby obtaining the pneumatic power of the centrifugal vapor compressor; and outputs the gas flow Q of the gas inlet at the accurate rotating speedinPressure p of exhaust gasoutAnd variable efficiency etapAnd the pneumatic power P, drawing a performance curve.
In step S2, inquiring the intake density, the intake entropy and the intake total enthalpy at a given intake temperature through the water vapor physical property parameter software; searching out the isentropic density and the isentropic total enthalpy of the exhaust according to the exhaust pressure and the intake entropy; and (5) searching the exhaust density according to the exhaust pressure and the total enthalpy of the exhaust.
In step S3, the flow coefficient is expressed as φ*，
The polytropic efficiency is expressed as etap *，
The head coefficient is denoted by psi*，
Wherein n represents the polytropic process exponent,
f is the coefficient of the polytropic pressure head,
nsin order to be an index of the isentropic process,
wherein QinRepresenting the gas flow rate of the inlet port, pinDenotes the gas density of the gas inlet, D2Denotes the diameter at the impeller exit, pinFor intake pressure, poutIs the discharge pressure, vinIs the specific volume of intake air, voutIs specific volume of exhaust gas, vout,sIs the specific volume of exhaust gas in the isentropic process, hinIs the total enthalpy of intake, houtIs the total enthalpy of exhaust, hout,sFor exhaust in isentropic processTotal enthalpy, N is rotational speed.
In step S4, the aerodynamic power is represented by P, and P ═ Qin*(hout-hin)。
In step S4, in step S4, based on the fact that the machine Mach number under the newly given operating condition is equal to the machine Mach number under the original design parameters of the centrifugal vapor compressor, the corresponding rotation speed under the newly given operating condition can be obtained,
M＝M*where M denotes the Mach number of the machine under the newly given operating conditions, M*Representing the machine Mach number u, at the original design parameters of the centrifugal vapor compressor2Indicating the peripheral speed at the impeller outlet at the corresponding rotational speed, u2 *For the peripheral speed at the impeller exit at the original design parameters of the centrifugal vapor compressor,
ainfor the inlet sound velocity at the newly given operating conditions, ain *Is the inlet sound velocity at the original design parameters of the centrifugal vapor compressor.
In step S4, in step S4, the energy head coefficient ψ and the polytropic efficiency η at the corresponding rotation speedpThe energy head coefficient and the polytropic efficiency of the centrifugal vapor compressor under the original design parameters of the centrifugal vapor compressor respectively have corresponding equivalent relations, namely psi ═ alpha ^ psi*，
Wherein psi*Representing the energy head coefficient, η, at the original design parameters of a centrifugal vapor compressorp *Expressing the polytropic efficiency of the centrifugal vapor compressor under the original design parameters, alpha and beta are empirical coefficients related to the inlet air temperature.
It is noted that, herein, relational terms such as first and second, and the like may be used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus.
The foregoing is merely an example of the present invention, and common general knowledge in the field of known specific structures and characteristics is not described herein in any greater extent than that known in the art at the filing date or prior to the priority date of the application, so that those skilled in the art can now appreciate that all of the above-described techniques in this field and have the ability to apply routine experimentation before this date can be combined with one or more of the present teachings to complete and implement the present invention, and that certain typical known structures or known methods do not pose any impediments to the implementation of the present invention by those skilled in the art. It should be noted that, for those skilled in the art, without departing from the structure of the present invention, several changes and modifications can be made, which should also be regarded as the protection scope of the present invention, and these will not affect the effect of the implementation of the present invention and the practicability of the patent. The scope of the claims of the present application shall be determined by the contents of the claims, and the description of the embodiments and the like in the specification shall be used to explain the contents of the claims.
Claims (6)
1. A centrifugal vapor compressor model selection method is characterized by comprising the following steps: the method comprises the following steps:
s1, calculating the exhaust pressure and the total exhaust enthalpy of the centrifugal vapor compressor under different flow rates according to the performance parameters of the centrifugal vapor compressor;
s2, inquiring the following performance parameters at the given air inlet temperature: the intake density, the intake entropy, the intake total enthalpy, the exhaust isentropic density, the exhaust isentropic total enthalpy and the exhaust density;
s3, carrying out non-dimensionalization on the performance parameters in the S2 to obtain a non-dimensionalized performance curve of the centrifugal steam compressor, wherein the non-dimensionalized performance curve comprises an energy head coefficient-flow coefficient curve and a polytropic efficiency-flow coefficient curve;
s4, determining the corresponding rotating speed under the new given operating condition; the new given operation conditions comprise an air inlet saturation temperature, a saturation temperature rise and a required flow; calculating the pressure ratio and the polytropic efficiency of the centrifugal steam compressor at the corresponding rotating speed according to the required flow in the newly given operating condition;
s5, comparing the pressure ratio calculated in S4 with the required pressure ratio, and adjusting the rotating speed to meet the requirement of the required pressure ratio, so as to obtain the accurate rotating speed under the newly given operating condition; calculating to obtain the exhaust pressure, the total exhaust enthalpy, the intake density, the intake entropy, the total intake enthalpy, the isentropic exhaust density, the total isentropic exhaust enthalpy and the exhaust density of the centrifugal vapor compressor at an accurate rotating speed, thereby obtaining the pneumatic power of the centrifugal vapor compressor; and outputting the gas flow, the exhaust pressure, the variable efficiency and the pneumatic power of the gas inlet at an accurate rotating speed, and drawing a performance curve.
2. A centrifugal vapor compressor sizing method according to claim 1, wherein: in step S2, inquiring the intake air density, the intake air entropy and the intake air total enthalpy at a given intake air temperature through the water vapor physical property parameter software; searching out the isentropic density and the isentropic total enthalpy of the exhaust according to the exhaust pressure and the intake entropy; and (5) searching the exhaust density according to the exhaust pressure and the total enthalpy of the exhaust.
3. A centrifugal vapor compressor sizing method according to claim 1, wherein: in step S3, the flow coefficient is expressed as φ*，
The polytropic efficiency is expressed as etap *，
The head coefficient is denoted by psi*，
Wherein n represents the polytropic process exponent,
f is the coefficient of the polytropic pressure head,
nsin order to be an index of the isentropic process,
wherein QinRepresenting the gas flow rate of the inlet port, pinDenotes the gas density of the gas inlet, D2Denotes the diameter at the impeller exit, pinFor intake pressure, poutIs the discharge pressure, vinIs the specific volume of intake air, voutIs specific volume of exhaust gas, vout,sIs the specific volume of exhaust gas in the isentropic process, hinIs the total enthalpy of intake, houtIs the total enthalpy of exhaust, hout,sThe total enthalpy of exhaust in the isentropic process, and N is the rotating speed.
4. A centrifugal vapor compressor sizing method according to claim 3, wherein: in step S4, the aerodynamic power is represented by P, and P ═ Qin*(hout-hin)。
5. A centrifugal vapor compressor sizing method according to claim 3, wherein: in step S4, the corresponding rotation speed under the newly given operating condition can be obtained according to the fact that the machine mach number under the newly given operating condition is equal to the machine mach number under the original design parameters of the centrifugal vapor compressor,
M＝M*where M denotes the Mach number of the machine under the newly given operating conditions, M*Representing the machine Mach number u, at the original design parameters of the centrifugal vapor compressor2Indicating the peripheral speed at the impeller outlet at the corresponding rotational speed, u2 *For the peripheral speed at the impeller exit at the original design parameters of the centrifugal vapor compressor,
ainfor the inlet sound velocity at the newly given operating conditions, ain *Is the inlet sound velocity at the original design parameters of the centrifugal vapor compressor.
6. A centrifugal vapor compressor sizing method according to claim 3, wherein: in step S4, the head coefficient ψ and the polytropic efficiency η at the corresponding rotation speedpThe energy head coefficient and the polytropic efficiency of the centrifugal vapor compressor under the original design parameters of the centrifugal vapor compressor respectively have corresponding equivalent relations, namely psi ═ alpha ^ psi*，
Wherein psi*Representing the energy head coefficient, η, at the original design parameters of a centrifugal vapor compressorp *Expressing the polytropic efficiency of the centrifugal vapor compressor under the original design parameters, alpha and beta are empirical coefficients related to the inlet air temperature.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010725814.7A CN111832189B (en) | 2020-07-24 | 2020-07-24 | Centrifugal vapor compressor model selection method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010725814.7A CN111832189B (en) | 2020-07-24 | 2020-07-24 | Centrifugal vapor compressor model selection method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111832189A CN111832189A (en) | 2020-10-27 |
| CN111832189B true CN111832189B (en) | 2021-09-14 |
Family
ID=72925411
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010725814.7A Active CN111832189B (en) | 2020-07-24 | 2020-07-24 | Centrifugal vapor compressor model selection method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN111832189B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113836659B (en) * | 2021-09-22 | 2024-01-30 | 西安石大派普特科技工程有限公司 | Method for characterizing performance characteristic color level chart of centrifugal compressor |
| CN115563726B (en) * | 2022-09-06 | 2023-06-06 | 重庆通用工业(集团)有限责任公司 | Type selection system and method for centrifugal steam compressor |
| CN117076830B (en) * | 2023-10-13 | 2024-03-12 | 中国空气动力研究与发展中心计算空气动力研究所 | Method and device for determining power of nitrogen axial flow compressor, electronic equipment and medium |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104156882A (en) * | 2014-07-10 | 2014-11-19 | 华南理工大学 | Method for calculating variable working condition of thermal power plant based on equivalent enthalpy drop and Friuli Greig formula |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1306193A (en) * | 2000-11-14 | 2001-08-01 | 王远春 | Method for drawing thermodynamic characteristics graph and table, its check method and its design calculation method |
| US6899075B2 (en) * | 2002-03-22 | 2005-05-31 | Roxan Saint-Hilaire | Quasiturbine (Qurbine) rotor with central annular support and ventilation |
| US20110160030A1 (en) * | 2009-12-17 | 2011-06-30 | Andreas Heilmann | Laboratory centrifuge with compressor cooling |
| DE102012002593A1 (en) * | 2012-02-13 | 2013-08-14 | Eppendorf Ag | Centrifuge with compressor cooling device and method for controlling a compressor cooling device of a centrifuge |
| CN104454531B (en) * | 2013-09-22 | 2016-02-03 | 珠海格力节能环保制冷技术研究中心有限公司 | The compression assembly of compressor, compressor and air conditioner |
| EP2980413A1 (en) * | 2014-07-29 | 2016-02-03 | L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude | An integrally-geared centrifugal compressor and a method for building an integrally-geared centrifugal compressor |
| CN104791601B (en) * | 2015-04-20 | 2017-01-18 | 中国石油化工股份有限公司青岛安全工程研究院 | Equipment selection method for CNG (compressed natural gas) filling substation |
| CN106286259B (en) * | 2016-10-14 | 2018-08-07 | 武汉理工大学 | A kind of vehicle fuel battery air compressor test system of ECU controls |
| CN109708261B (en) * | 2019-01-22 | 2020-07-10 | 顿汉布什(中国)工业有限公司 | Optimized model selection method for configuration of two-stage centrifugal unit |
| CN110005635B (en) * | 2019-01-28 | 2020-08-28 | 天津大学 | Design method of impeller |
| CN111027148B (en) * | 2019-10-28 | 2023-07-04 | 西安陕鼓动力股份有限公司 | Automatic calibration and industrial axial flow compressor performance calculation method for loss lag angle model |
-
2020
- 2020-07-24 CN CN202010725814.7A patent/CN111832189B/en active Active
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104156882A (en) * | 2014-07-10 | 2014-11-19 | 华南理工大学 | Method for calculating variable working condition of thermal power plant based on equivalent enthalpy drop and Friuli Greig formula |
Also Published As
| Publication number | Publication date |
|---|---|
| CN111832189A (en) | 2020-10-27 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN111832189B (en) | Centrifugal vapor compressor model selection method | |
| CN201090462Y (en) | Enclosed high energy head model level | |
| CN109684597B (en) | Method for expanding all-condition characteristics of gas compressor | |
| CN114444331B (en) | Stage characteristic matching method of multistage axial flow compressor | |
| Elder et al. | A discussion of the factors affecting surge in centrifugal compressors | |
| Harley et al. | Assessing 1D loss models for the off-design performance prediction of automotive turbocharger compressors | |
| Chu et al. | A model for parameter estimation of multistage centrifugal compressor and compressor performance analysis using genetic algorithm | |
| CN113297705A (en) | Method for predicting characteristics of gas compressor according to design indexes | |
| CN109635512B (en) | Centrifugal impeller inlet design method based on correction control equation | |
| Liang et al. | Design of a centrifugal compressor with low solidity vaned diffuser (LSVD) for large-scale compressed air energy storage (CAES) | |
| Rajoo et al. | Variable geometry mixed flow turbine for turbochargers: an experimental study | |
| Swain | Improving a one-dimensional centrifugal compressor performance prediction method | |
| Li et al. | Design of a novel axial impeller as a part of counter-rotating axial compressor to compress water vapor as refrigerant | |
| Yu et al. | Numerical Investigation of the Effect of Diffuser and Volute Design Parameters on the Performance of a Centrifugal Compressor Stage | |
| Wang et al. | Numerical simulation and validation of effects of blade inlet angle on performance of pump-as-turbine | |
| CN112528397A (en) | Optimized design method for rear fluid director of jet fan | |
| CN109446745A (en) | A kind of design method of helium compressor one-dimensional aerodynamic | |
| CN115563726B (en) | Type selection system and method for centrifugal steam compressor | |
| Ziegler et al. | Development of a Novel Axial Compressor Generation for Industrial Applications: Part 1—Compressor Design and Performance | |
| Wang et al. | Research on Optimal Matching Method of Variable Stator Vanes for Multi-Stage Compressor Based on Genetic Algorithm | |
| CN117744283B (en) | Design method, device, equipment and computer storage medium for compressor | |
| CN107939664B (en) | The starting with pressure of LNG compressor set determines system | |
| Waluyo et al. | Performance analysis off-design centrifugal compressor performance through numerical simulation | |
| Jang et al. | Performance Characteristics on Turbo Blowers Connected in Serial and Controlled by Inverter | |
| Eckert et al. | Design of a Centrifugal Turbo Compressor With the Working Fluid Water for the Operation in a Hybrid Sorption/Compression Heat Pump Cycle |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |