CN108533525B - Centrifugal impeller based on maximum stream flow coefficient prewhirl air inlet enthalpy rise coefficient calculation method - Google Patents
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Abstract
A kind of centrifugal impeller based on maximum stream flow coefficient air inlet enthalpy of prewhirling rises coefficient calculation method: determining the design requirement of centrifugal impeller；The characteristic constant of given fluid media (medium) and the geometric constant of centrifugal impeller；Calculate the outlet tangential velocity ratio of centrifugal impeller；It sets initial enthalpy and rises coefficient；Computing machine Mach number；Set initial centrifugation impeller inlet wheel cap relative Mach number；Calculate centrifugal impeller import wheel cap flow angle to axial；Calculate centrifugal impeller import wheel cap relative Mach number；Judge whether the relative error of the initial centrifugation impeller inlet wheel cap relative Mach number of centrifugal impeller import wheel cap relative Mach number and setting is less than setting value；Calculate the ratio of centrifugal impeller import shroud diameter and centrifugal impeller outlet diameter；It calculates enthalpy and rises coefficient；Judge whether the relative error of the initial enthalpy liter coefficient of enthalpy liter coefficient and setting is less than setting value.The enthalpy that the present invention accurately can quickly calculate the big flow centrifugal impeller arbitrarily prewhirled under flow inlet angle rises coefficient, and the centrifugal impeller flow produced is big, compact-sized.
Description
Technical Field
The invention relates to a method for calculating an enthalpy rise coefficient of an arbitrary pre-rotation air inlet angle of a centrifugal impeller. In particular to a centrifugal impeller pre-rotation air inlet enthalpy rising coefficient calculation method based on a maximum flow coefficient.
Background
The centrifugal compressor is widely applied to aeroengines, ground gas turbines, automobile and ship turbochargers and petrochemical compressors, and plays an irreplaceable role in the fields of national defense, civil industry and the like. The centrifugal impeller is used as a core component of the centrifugal compressor, and an accurate thermodynamic calculation and design method of the centrifugal impeller is a key technology. The accurate calculation of the enthalpy rise coefficient of the centrifugal impeller is the basis for breaking through the key technology. For a centrifugal impeller with a given machine Mach number, the enthalpy rise coefficient, the total pressure ratio and the isentropic efficiency have quantitative relations, and accurate estimation of the enthalpy rise coefficient is of great importance to the design of the centrifugal impeller. Currently, in most centrifugal impeller thermodynamic calculations and designs, the enthalpy rise coefficient is specified as a constant, or only the impeller outlet geometric influence (slip factor) is considered, which results in a large deviation of the enthalpy rise coefficient calculation result from the actual value. Moreover, research is only carried out on axial air inlet conditions, any pre-swirl air inlet is not considered, and the influence of geometric constraint on enthalpy rise coefficients is not considered. In fact, for a given impeller speed, the axial inlet conditions are determined primarily by the impeller exit geometry (blade sweep angle, etc.), and for pre-swirl inlet conditions it is also related to the impeller inlet geometry (blade leading edge form factor, aerodynamic throat area, etc.). Therefore, an enthalpy rise coefficient calculation method which comprehensively considers various influence factors is provided, and accurate enthalpy rise coefficient acquisition is an urgent task for centrifugal impeller thermodynamic calculation and design technology.
Disclosure of Invention
The invention aims to solve the technical problem of providing a centrifugal impeller prerotation air inlet enthalpy rise coefficient calculation method which can accurately calculate the thermodynamic properties (isentropic efficiency, total pressure ratio and the like) of a centrifugal impeller and is based on a maximum flow coefficient and is designed initially.
The technical scheme adopted by the invention is as follows: a centrifugal impeller pre-rotation air inlet enthalpy rising coefficient calculation method based on a maximum flow coefficient comprises the following steps:
1) determining design requirements for a centrifugal impeller comprising: the isentropic efficiency eta, the total pressure ratio epsilon and the flow coefficient phi;
2) respectively setting a characteristic constant of the fluid medium and a geometric constant of the centrifugal impeller;
3) calculating the outlet tangential velocity ratio of a centrifugal impeller
4) Setting initial enthalpy rise coefficient mu0；
5) Computing machine Mach number Mu2；
6) Setting relative Mach number M of inlet shroud of initial centrifugal impellerw1,0；
7) Calculating the relative axial airflow angle beta of the inlet wheel cover of the centrifugal impeller1s；
8) Calculating relative Mach number M of inlet wheel cover of centrifugal impellerw1；
9) Judging relative Mach number M of inlet wheel cover of centrifugal impellerw1Relative Mach number M of inlet shroud of initial centrifugal impeller setw1,0If the relative error is less than 1%, executing the next step, otherwise, returning to the step 6), and resetting the relative Mach number M of the inlet wheel cover of the initial centrifugal impeller by adopting a dichotomyw1,0；
10) Calculating the diameter D of the inlet wheel cover of the centrifugal impeller1sAnd diameter D of centrifugal impeller outlet2The ratio of (A) to (B):
11) calculating an enthalpy rise coefficient mu;
12) judging the enthalpy rise coefficient mu and the set initial enthalpy rise coefficient mu0If the relative error is less than 1%, if so, mu is the enthalpy rise coefficient to be obtained, and ending; otherwise, returning to the step 4) and resetting the initial enthalpy rise coefficient mu by adopting a dichotomy0。
The characteristic constants of the fluid medium in the step 2) are as follows: a gas constant R and an adiabatic index γ; the geometric constant of the centrifugal impeller; the method comprises the following steps: shape factor k, centrifugal impeller exit radial velocity ratioRadial air flow angle beta at centrifugal impeller outlet2Inlet prerotation angle alpha of centrifugal impeller1The number of blades z, and the specific enthalpy ratio σ.
The calculation formula of the shape factor k is as follows:wherein D is1hIs the diameter of the inlet hub of the centrifugal impeller, D1sIs the diameter of the inlet shroud of the centrifugal impeller.
The calculation formula of the specific enthalpy ratio sigma is as follows:wherein h istotIs the total work of the centrifugal impeller, hthIs the rim work of the centrifugal impeller.
Step 3) calculating the outlet tangential velocity ratio of the centrifugal impeller by using the Sjordola formulaThe following were used:
in the formula,is the radial velocity ratio, beta, of the centrifugal impeller outlet2Is the centrifugal impeller outlet radial airflow angle.
Step 5) calculating the Mach number M of the machine by adopting the following formulau2：
Where γ is the adiabatic index, η is the isentropic efficiency, ε is the total pressure ratio, μ0Is the initial enthalpy rise coefficient.
Step 7) calculating the relative axial airflow angle beta of the inlet wheel cover of the centrifugal impeller by adopting the following formula1s
In the formula, alpha1Is the inlet prerotation angle of centrifugal impeller, Mw1,0Is the relative mach number of the inlet shroud of the initial centrifugal impeller and gamma is the adiabatic index.
Step 8) calculating the relative Mach number M of the inlet wheel cover of the centrifugal impeller by adopting the following formulaw1
In the formula, Mu2Is the machine Mach number, gamma is the adiabatic index, Mw1,0Is the relative Mach number, beta, of the inlet shroud of the initial centrifugal impeller1sIs the relative axial flow angle, alpha, of the inlet shroud of the centrifugal impeller1Is the centrifugal impeller inlet prewhirl angle, k is the shape factor and phi is the flow coefficient.
Step 10), the diameter ratio of the inlet wheel cover of the centrifugal impeller to the outlet of the centrifugal impeller is as follows:
in the formula, Mw1Is the relative Mach number, beta, of the inlet shroud of the centrifugal impeller1sIs the relative axial flow angle, alpha, of the inlet shroud of the centrifugal impeller1Is the prerotation angle of centrifugal impeller inlet, eta is the isentropic efficiency, mu0Is the initial enthalpy rise coefficient, gamma is the adiabatic exponent, and epsilon is the total pressure ratio.
Step 11) is to calculate the enthalpy rise coefficient μ using the following formula
Wherein, σ is a specific enthalpy ratio,is the outlet tangential velocity ratio of the centrifugal impeller, gamma is the adiabatic index, Mw1Is the relative Mach number, beta, of the inlet shroud of the centrifugal impeller1sIs the relative axial flow angle, alpha, of the inlet shroud of the centrifugal impeller1Is the centrifugal impeller inlet prewhirl angle, k is the form factor,is the ratio of the diameter of the inlet shroud of the centrifugal impeller to the diameter of the outlet of the centrifugal impeller, Mu2Is the machine mach number.
The centrifugal impeller pre-rotation air inlet enthalpy rising coefficient calculation method based on the maximum flow coefficient considers any pre-rotation air inlet angle, and popularizes the traditional method only comprising axial air inlet; meanwhile, the method provided by the invention comprises the assumption of the maximum flow coefficient, and the designed centrifugal impeller has the advantages of large flow, compact structure and the like; the calculation expressions are in dimensionless form and have universality. The method has the advantages that the enthalpy rise coefficient of the large-flow centrifugal impeller under any pre-rotation air inlet angle can be accurately and quickly calculated, and a foundation is laid for evaluating the performance of the existing impeller or developing a new impeller.
Detailed Description
The method for calculating the enthalpy-rise coefficient of the pre-swirl intake air of the centrifugal impeller based on the maximum flow coefficient according to the present invention is described in detail with reference to the following embodiments, which are descriptive and not intended to limit the scope of the present invention.
The method for calculating the enthalpy rise coefficient of the pre-rotation inlet air of the centrifugal impeller based on the maximum flow coefficient introduces the design concept of the maximum flow coefficient by considering any pre-rotation inlet angle, and provides a dimensionless enthalpy rise coefficient calculation method; and finally, according to the design condition of the centrifugal impeller, giving a specific step of enthalpy rise coefficient calculation.
The invention discloses a centrifugal impeller pre-rotation air inlet enthalpy rising coefficient calculation method based on a maximum flow coefficient, which specifically comprises the following steps:
1) determining design requirements for a centrifugal impeller comprising: the isentropic efficiency eta, the total pressure ratio epsilon and the flow coefficient phi;
2) respectively setting a characteristic constant of the fluid medium and a geometric constant of the centrifugal impeller; wherein,
the characteristic constants of the fluid medium are: a gas constant R and an adiabatic index γ; the geometric constant of the centrifugal impeller; the method comprises the following steps: shape factor k, centrifugal impeller exit radial velocity ratioRadial air flow angle beta at centrifugal impeller outlet2Inlet prerotation angle alpha of centrifugal impeller1The number of blades z, and the specific enthalpy ratio σ.
The calculation formula of the shape factor k is as follows:wherein D is1hIs the diameter of the inlet hub of the centrifugal impeller, D1sIs the diameter of the inlet shroud of the centrifugal impeller.
The calculation formula of the specific enthalpy ratio sigma is as follows:wherein h istotIs the total work of the centrifugal impeller, hthIs the rim work of the centrifugal impeller.
3) Calculating the outlet tangential velocity ratio of a centrifugal impellerThe outlet tangential velocity ratio of the centrifugal impeller is calculated by using the formula of SjotraThe following were used:
in the formula,is the radial velocity ratio, beta, of the centrifugal impeller outlet2Is the centrifugal impeller outlet radial airflow angle.
4) Setting initial enthalpy rise coefficient mu0；
5) Computing machine Mach number Mu2(ii) a The Mach number M of the machine is calculated by adopting the following formulau2：
Where γ is the adiabatic index, η is the isentropic efficiency, ε is the total pressure ratio, μ0Is the initial enthalpy rise coefficient.
6) Setting relative Mach number M of inlet shroud of initial centrifugal impellerw1,0；
7) Calculating the relative axial airflow angle beta of the inlet wheel cover of the centrifugal impeller1s(ii) a Is the best beta obtained based on the assumption of the maximum flow coefficient1s(ii) a Specifically, the relative axial airflow angle beta of the inlet wheel cover of the centrifugal impeller is calculated by adopting the following formula1sIt is in implicit format, using iterative computation:
in the formula, alpha1Is the inlet prerotation angle of centrifugal impeller, Mw1,0Is the relative mach number of the inlet shroud of the initial centrifugal impeller and gamma is the adiabatic index.
8) ComputingRelative mach number M of inlet shroud of centrifugal impellerw1(ii) a The relative Mach number M of the inlet wheel cover of the centrifugal impeller is calculated by adopting the following formulaw1：
In the formula, Mu2Is the machine Mach number, gamma is the adiabatic index, Mw1,0Is the relative Mach number, beta, of the inlet shroud of the initial centrifugal impeller1sIs the relative axial flow angle, alpha, of the inlet shroud of the centrifugal impeller1Is the centrifugal impeller inlet prewhirl angle, k is the shape factor and phi is the flow coefficient.
9) Judging relative Mach number M of inlet wheel cover of centrifugal impellerw1Relative Mach number M of inlet shroud of initial centrifugal impeller setw1,0If the relative error is less than 1%, executing the next step; otherwise, returning to the step 6) to reset the relative Mach number M of the inlet wheel cover of the initial centrifugal impeller by adopting a dichotomyw1,0；
10) Calculating the diameter D of the inlet wheel cover of the centrifugal impeller1sAnd diameter D of centrifugal impeller outlet2The ratio of:the diameter ratio of the inlet wheel cover of the centrifugal impeller to the outlet of the centrifugal impeller is as follows:
in the formula, Mw1Is the relative Mach number, beta, of the inlet shroud of the centrifugal impeller1sIs the relative axial flow angle, alpha, of the inlet shroud of the centrifugal impeller1Is the prerotation angle of centrifugal impeller inlet, eta is the isentropic efficiency, mu0Is the initial enthalpy rise coefficient, gamma is the adiabatic exponent, and epsilon is the total pressure ratio.
11) Calculating an enthalpy rise coefficient mu; the enthalpy rise coefficient mu is calculated by adopting the following formula
12) Judging the enthalpy rise coefficient mu and the set initial enthalpy rise coefficient mu0If the relative error is less than 1%, if so, mu is the enthalpy rise coefficient to be obtained, and ending; otherwise, returning to the step 4) and resetting the initial enthalpy rise coefficient mu by adopting a dichotomy0。
Specific examples are given below:
the embodiment combines a design process demonstration calculation enthalpy rise coefficient method of an industrial transonic centrifugal impeller, whereinCalculated according to the formula of Sjordan, namely the formula (1). The enthalpy rise coefficient was calculated by the following 12 steps:
1) determining the design requirement of a centrifugal impeller: the isentropic efficiency eta is 0.87, the total pressure ratio epsilon is 6, and the flow coefficient phi is 0.15
2) Given the constant k ═ 0.85, R ═ 287, γ ═ 1.4,β2＝38,z＝13,σ＝1.07,α1＝30deg
3) calculating according to equation (1)
4) Assuming an initial enthalpy rise coefficient μ0＝0.7
5) Computing machine Mach number M according to equation (2)u2＝1.65659
6) Assume initial Mw1,0＝1.1
7) Calculating beta according to equation (3)1sFinal result of beta1s＝45.33
8) Calculating M according to equation (4)w1The final result Mw1＝1.204528
9) Check Mw1If the iteration precision is satisfied, executing the next step, otherwise, returning to 6) correcting Mw1,0
10) Calculating according to equation (5)End result
11) The enthalpy rise coefficient μ is calculated according to formula (6), and the final result μ is 0.541745
12) Checking the enthalpy rise coefficient mu, if the iteration precision is met, finishing the calculation, otherwise, returning to 4) correcting the mu0。
Therefore, the maximum flow coefficient is calculated to design any pre-rotation air inlet angle enthalpy rise coefficient of the centrifugal impeller, and the method can be used as the basis of thermodynamic calculation or brand new design of the centrifugal impeller.
Claims (10)
1. A centrifugal impeller pre-rotation air inlet enthalpy rising coefficient calculation method based on a maximum flow coefficient is characterized by comprising the following steps:
1) determining design requirements for a centrifugal impeller comprising: the isentropic efficiency eta, the total pressure ratio epsilon and the flow coefficient phi;
2) respectively setting a characteristic constant of the fluid medium and a geometric constant of the centrifugal impeller;
3) calculating the outlet tangential velocity ratio of a centrifugal impeller
4) Setting initial enthalpy rise coefficient mu0；
5) Computing machine Mach number Mu2；
6) Setting relative Mach number M of inlet shroud of initial centrifugal impellerw1,0；
7) Calculating the relative axial airflow angle beta of the inlet wheel cover of the centrifugal impeller1s；
8) Calculating relative Mach number M of inlet wheel cover of centrifugal impellerw1；
9) Judging relative Mach number M of inlet wheel cover of centrifugal impellerw1Relative Mach number M of inlet shroud of initial centrifugal impeller setw1,0If the relative error is less than 1%, executing the next step, otherwise, returning to the step 6), and resetting the initial centrifugal impeller by adopting a dichotomyRelative mach number M of port wheel coverw1,0；
10) Calculating the diameter D of the inlet wheel cover of the centrifugal impeller1sAnd diameter D of centrifugal impeller outlet2The ratio of (A) to (B):
11) calculating an enthalpy rise coefficient mu;
12) judging the enthalpy rise coefficient mu and the set initial enthalpy rise coefficient mu0If the relative error is less than 1%, if so, mu is the enthalpy rise coefficient to be obtained, and ending; otherwise, returning to the step 4) and resetting the initial enthalpy rise coefficient mu by adopting a dichotomy0。
2. The method for calculating the enthalpy rise coefficient of pre-swirl intake air of a centrifugal impeller based on the maximum flow coefficient according to claim 1, wherein the characteristic constants of the fluid medium in step 2) are: a gas constant R and an adiabatic index γ; the geometric constant of the centrifugal impeller; the method comprises the following steps: shape factor k, centrifugal impeller exit radial velocity ratioRadial air flow angle beta at centrifugal impeller outlet2Inlet prerotation angle alpha of centrifugal impeller1The number of blades z, and the specific enthalpy ratio σ.
3. The method for calculating the enthalpy rise coefficient of pre-swirl intake air of a centrifugal impeller based on the maximum flow coefficient of claim 2, wherein the shape factor k is calculated by the following formula:wherein D is1hIs the diameter of the inlet hub of the centrifugal impeller, D1sIs the diameter of the inlet shroud of the centrifugal impeller.
4. The method for calculating the enthalpy-rise coefficient of pre-swirl intake air of a centrifugal impeller based on the maximum flow coefficient of claim 2, wherein the specific enthalpy ratio σ isThe calculation formula is as follows:wherein h istotIs the total work of the centrifugal impeller, hthIs the rim work of the centrifugal impeller.
5. The method for calculating the enthalpy rise coefficient of pre-swirl intake air of a centrifugal impeller based on the maximum flow coefficient of claim 1, wherein the step 3) is to calculate the outlet tangential velocity ratio of the centrifugal impeller by using the Strorado formulaThe following were used:
in the formula,is the radial velocity ratio, beta, of the centrifugal impeller outlet2Is the centrifugal impeller exit radial airflow angle and z is the number of blades.
6. The method for calculating the enthalpy-rise coefficient of pre-whirling intake air of the centrifugal impeller according to claim 1, wherein the step 5) is to calculate the Mach number M of the machine by using the following formulau2：
Where γ is the adiabatic index, η is the isentropic efficiency, ε is the total pressure ratio, μ0Is the initial enthalpy rise coefficient.
7. The method for calculating the enthalpy-rise coefficient of pre-swirl inlet air of a centrifugal impeller according to claim 1, wherein step 7) is to calculate the relative axial air of the inlet shroud of the centrifugal impeller by using the following formulaFlow angle beta1s
In the formula, alpha1Is the inlet prerotation angle of centrifugal impeller, Mw1,0Is the relative mach number of the inlet shroud of the initial centrifugal impeller and gamma is the adiabatic index.
8. The method for calculating the enthalpy-rise coefficient of pre-swirl intake air of a centrifugal impeller according to claim 1, wherein the step 8) is to calculate the relative mach number M of the inlet shroud of the centrifugal impeller by using the following formulaw1
In the formula, Mu2Is the machine Mach number, gamma is the adiabatic index, Mw1,0Is the relative Mach number, beta, of the inlet shroud of the initial centrifugal impeller1sIs the relative axial flow angle, alpha, of the inlet shroud of the centrifugal impeller1Is the centrifugal impeller inlet prewhirl angle, k is the shape factor and phi is the flow coefficient.
9. The method for calculating the enthalpy rise coefficient of pre-swirl intake air of a centrifugal impeller according to claim 1, wherein the ratio of the diameter of the inlet shroud of the centrifugal impeller to the diameter of the outlet of the centrifugal impeller in step 10) is as follows:
in the formula, Mw1Is the relative Mach number, beta, of the inlet shroud of the centrifugal impeller1sIs the relative axial flow angle, alpha, of the inlet shroud of the centrifugal impeller1Is the prerotation angle of centrifugal impeller inlet, eta is the isentropic efficiency, mu0Is the initial enthalpy rise coefficient, gamma is the adiabatic exponent, and epsilon is the total pressure ratio.
10. The method for calculating the enthalpy-rise coefficient of pre-swirl intake air of a centrifugal impeller based on the maximum flow coefficient of claim 1, wherein step 11) is to calculate the enthalpy-rise coefficient μ using the following formula
Wherein, σ is a specific enthalpy ratio,is the outlet tangential velocity ratio of the centrifugal impeller, gamma is the adiabatic index, Mw1Is the relative Mach number, beta, of the inlet shroud of the centrifugal impeller1sIs the relative axial flow angle, alpha, of the inlet shroud of the centrifugal impeller1Is the centrifugal impeller inlet prewhirl angle, k is the form factor,is the ratio of the diameter of the inlet shroud of the centrifugal impeller to the diameter of the outlet of the centrifugal impeller, Mu2Is the machine mach number.
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN101980230A (en) * | 2010-11-03 | 2011-02-23 | 天津大学 | Catalytic cracking reaction system process simulation optimization model and solution method thereof |
| CN103244292A (en) * | 2012-02-02 | 2013-08-14 | 福特环球技术公司 | Method for influencing the thermal balance of an internal combustion engine |
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Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN101980230A (en) * | 2010-11-03 | 2011-02-23 | 天津大学 | Catalytic cracking reaction system process simulation optimization model and solution method thereof |
| CN103244292A (en) * | 2012-02-02 | 2013-08-14 | 福特环球技术公司 | Method for influencing the thermal balance of an internal combustion engine |
Non-Patent Citations (1)
| Title |
|---|
| 目标优化算法在叶片参数化设计中的应用;刘正先等;《天津大学学报》;20170131;第50卷(第1期);第19-27 * |
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