CN116451364A - Design method of hydraulic turbine impeller splitter blade - Google Patents
Design method of hydraulic turbine impeller splitter blade Download PDFInfo
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- CN116451364A CN116451364A CN202310260715.XA CN202310260715A CN116451364A CN 116451364 A CN116451364 A CN 116451364A CN 202310260715 A CN202310260715 A CN 202310260715A CN 116451364 A CN116451364 A CN 116451364A
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- 238000004364 calculation method Methods 0.000 claims description 11
- 239000007788 liquid Substances 0.000 claims description 10
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
- F03B3/12—Blades; Blade-carrying rotors
- F03B3/121—Blades, their form or construction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
- F03B3/12—Blades; Blade-carrying rotors
- F03B3/125—Rotors for radial flow at high-pressure side and axial flow at low-pressure side, e.g. for Francis-type turbines
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- 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
- G06F30/28—Design optimisation, verification or simulation using fluid dynamics, e.g. using Navier-Stokes equations or computational fluid dynamics [CFD]
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- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces
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- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
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- Computational Mathematics (AREA)
- Hydraulic Turbines (AREA)
Abstract
The invention discloses a design method of a hydraulic turbine impeller splitter blade, which comprises the following steps: determining inlet setting angles of the main blades, forming a flow channel between adjacent main blades, wherein the inlet of the splitter blade is consistent with the inlet setting angle of the main blade; step two: determining the length and offset angle of the splitter blade; step three: determining the setting angle of the outlet of the splitter blade; step four: determining an inlet sweep angle of the splitter blade; step five: the inlet and the outlet of the split flow inlet are connected, so that the surface from the inlet to the outlet of the split flow blade is smooth and continuous. According to the method, the number of the effective blades is increased under the condition that the inlet of the blades is not increased, so that fluid flows more uniformly along the impeller flow channel, flow separation and secondary flow caused by high-speed rotation inside the impeller flow channel are reduced, flow field distribution inside the impeller is improved, the area and strength of vortex inside the impeller are reduced, the energy recovery efficiency and the operation stability of the hydraulic turbine are improved, the hydraulic efficiency of the turbine is improved, and the range of a high-efficiency area is widened.
Description
Technical Field
The invention belongs to the technical field of energy conservation, emission reduction and miniature hydroelectric generation, and particularly relates to a design method of a hydraulic turbine impeller splitter blade.
Background
In the industrial processes of petrochemical industry, sea water desalination, urban water supply network and the like, a large amount of residual pressure energy exists, the residual pressure energy is directly decompressed through a pore plate or a decompression valve, the energy is wasted, and the waste of the residual pressure energy can be avoided by replacing the decompression device with the energy recovery device. The centrifugal pump turbine (pump turbine or hydraulic turbine for short) is a technically and economically effective energy recovery mode, and compared with the traditional water turbine, the pump turbine has the advantages of simple structure, low cost, convenient operation and maintenance, high economical efficiency and the like. The pump is used as a turbine technology to generate electricity in remote rural areas, so that the method is economically feasible, and the living quality of local people can be effectively improved.
Because the performance of the original centrifugal pump after directly reversing the pump as a turbine can not be accurately predicted, and the efficiency of the pump as the turbine is generally not higher than the efficiency of the pump working condition, in addition, the pump as the turbine has the problems of noise and vibration in actual operation, the safe and stable operation of a unit is affected, and enterprises are generally reluctant to install an energy recovery device in an industrial process based on the requirement of high reliability of the system. The factors objectively limit the popularization and the application of the hydraulic turbine energy-saving technology in the recovery of industrial residual pressure energy. The prior applicant develops a special impeller for a turbine, which is specially suitable for reverse running of a pump, not only remarkably improves the running efficiency of a hydraulic turbine, but also solves the problem of inaccurate prediction of a high-efficiency point of the running of the turbine. However, because the water flows into the impeller asymmetrically in the circumferential direction, even under the design working condition, the impeller still generates non-ideal flows such as axial vortexes, secondary flows and the like, and different forms of vortical movements are formed in the impeller flow channel, so that unstable flows of the fluid are caused, and the energy loss of the fluid is further increased, and therefore, in order to further improve the efficiency and the operation stability of the hydraulic turbine, the unstable flows in the impeller special for the turbine are required to be improved.
Accordingly, there is a need for a method of designing a splitter vane for a hydraulic turbine wheel that addresses the above issues.
Disclosure of Invention
In order to solve the technical problems, the invention provides a design method of a hydraulic turbine impeller splitter blade, wherein splitter blades are arranged among main blades, and reasonable length, offset angle, inlet sweep angle, outlet velocity moment and splitter blade setting angle change rules of the splitter blades are determined to improve the performance of a turbine.
In order to achieve the above object, the present invention provides a method for designing a splitter blade of a hydraulic turbine, comprising the steps of:
step one: determining inlet setting angles of the main blades, forming a flow channel between adjacent main blades, wherein the inlet of the splitter blade is consistent with the inlet setting angle of the main blade;
step two: determining the length and offset angle of the splitter blade;
step three: determining the setting angle of the outlet of the splitter blade; calculating the efficiency of the turbine when the outlet speed moment is positive, zero and negative respectively, and further determining the setting angle of the outlet of the splitter blade;
step four: determining an inlet sweep angle of the splitter blade; calculating the efficiency of the turbine when the inlet sweep angle is positive, zero and negative respectively, thereby determining the inlet sweep angle;
step five: the inlet and the outlet of the splitter blade are connected, so that the surface from the inlet to the outlet of the splitter blade is smooth and continuous.
Preferably, in the third step, the outlet velocity moment of the splitter blade is negative, and the outlet velocity moment of the splitter blade is-1% -4% of the inlet velocity moment, at this time, the absolute velocity of the outlet in the outlet velocity triangle has a circumferential component velocity opposite to the rotation direction of the impeller, so that a calculation formula of the liquid flow angle at the outlet of the splitter blade can be obtained:
wherein,,
substituting the flow angle into the formula to obtain the flow angle of the outlet of the splitter blade, wherein the flow angle of the outlet of the splitter blade is calculated by the formula:
wherein beta is 2 For the splitter vane outlet flow angle; q (Q) r Calculating flow for the design working point; a is that 2 In order to consider the actual axial surface flow water cross-section area on the circumference of the water outlet edge of the splitter blade after the splitter blade is added; u (u) 2 Is the peripheral velocity of the liquid at the outlet edge of the splitter vane; v m2 The absolute velocity at the outlet of the splitter vane is the split velocity in the direction of the axial plane.
Preferably, in the third step, the calculating formula of the setting angle of the outlet of the splitter blade is as follows:
β b2 ＝β 2 (4)
wherein beta is b2 The angle at which the splitter blade exits.
Preferably, in the formula
Wherein D is 2 The diameter of the water outlet edge of the splitter blade is related to the length of the splitter blade; n is the rotational speed of the impeller.
Preferably, the inlet sweep angle of the splitter blade is negative, and takes a value of-2 DEG to-6 deg.
Preferably, the thickness of the inlet of the splitter blade is larger than that of the outlet, and the surface of the splitter blade is smooth.
Preferably, the length of the main blade is L, and the length of the splitter blade is 0.5L-0.8L.
Preferably, the included angle of adjacent main blades is theta, and the offset angle of the splitter blade is 0.4 theta-0.6 theta.
Compared with the prior art, the invention has the following advantages and technical effects: the invention discloses a design method of a hydraulic turbine impeller splitter blade, wherein splitter blades are arranged among main blades, and the performance of a turbine is improved by calculating and determining the length, offset angle, inlet sweep angle, outlet velocity moment and splitter blade setting angle change rule of the splitter blades. According to the method, the number of the effective blades is increased under the condition that the inlet of the blades is not increased, so that fluid flows more uniformly along the impeller flow channel, flow separation and secondary flow caused by high-speed rotation inside the impeller flow channel are reduced, flow field distribution inside the impeller is improved, the area and strength of vortex inside the impeller are reduced, the energy recovery efficiency and the operation stability of the hydraulic turbine are improved, the hydraulic efficiency of the turbine is improved, and the range of a high-efficiency area is widened.
Drawings
The accompanying drawings, which are included to provide a further understanding of the application, illustrate and explain the application and are not to be construed as limiting the application. In the drawings:
FIG. 1 is a flow chart of a method of designing a splitter vane of a hydraulic turbine wheel according to the present invention;
FIG. 2 is a schematic length view of a splitter blade according to the present invention;
FIG. 3 is a schematic view of the offset angle of the splitter blade of the present invention;
FIG. 4 is a schematic view of the inlet sweep of a splitter blade according to the present invention;
FIG. 5 shows the variation between the inlet and outlet of the splitter vane of the present invention;
FIG. 6 is a diagram comparing the internal flow field of the impeller of the present invention with that of the prior art;
FIG. 7 is a graph of the two turbine operating characteristics of the present invention versus a conventional impeller;
FIG. 8 is a splitter vane exit velocity triangle of the present invention;
in the figure: 1. a main blade; 2. and a splitter blade.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
In order that the above-recited objects, features and advantages of the present invention will become more readily apparent, a more particular description of the invention will be rendered by reference to the appended drawings and appended detailed description.
Referring to FIGS. 1-8, the present embodiment provides a method of designing a splitter blade for a hydraulic turbine, comprising the steps of:
step one: determining inlet setting angles of the main blades 1, forming a flow channel between adjacent main blades 1, wherein the inlet of the splitter blade 2 is consistent with the inlet setting angle of the main blade 1;
step two: determining splitter blades 2 length and offset angle;
step three: determining the setting angle of the outlet of the splitter blade 2; the efficiency of the turbine when the outlet speed moment is positive, zero and negative is calculated respectively, and then the setting angle of the outlet of the splitter blade 2 is determined;
step four: determining the inlet sweep angle of the splitter blade 2; calculating the efficiency of the turbine when the inlet sweep angle is positive, zero and negative respectively, thereby determining the inlet sweep angle;
step five: the inlet and the outlet of the splitter blade 2 are connected, so that the surface from the inlet to the outlet of the splitter blade 2 is smooth and continuous.
The invention discloses a design method of a hydraulic turbine impeller splitter blade, which is characterized in that splitter blades 2 are arranged among main blades 1, and reasonable length, offset angle, inlet sweep angle, outlet velocity moment and placement angle change rule of the splitter blades 2 are determined to improve the performance of a turbine. According to the method, the number of the effective blades is increased under the condition that the inlet of the blades is not increased, so that fluid flows more uniformly along the impeller flow channel, flow separation and secondary flow caused by high-speed rotation inside the impeller flow channel are reduced, flow field distribution inside the impeller is improved, the area and strength of vortex inside the impeller are reduced, the energy recovery efficiency and the operation stability of the hydraulic turbine are improved, the hydraulic efficiency of the turbine is improved, and the range of a high-efficiency area is widened.
According to a further optimization scheme, the outlet speed moment of the splitter blade 2 is negative, the outlet speed moment of the splitter blade 2 is-1% -4% of the inlet speed moment, at the moment, the absolute speed of the outlet in the outlet speed triangle has a circumferential component speed opposite to the rotation direction of the impeller, and a liquid flow angle calculation formula at the outlet of the splitter blade 2 can be obtained:
wherein,,
substituting the formula (2) into the formula (1) to obtain the calculation formula of the outlet liquid flow angle of the splitter blade 2, wherein the calculation formula is as follows:
wherein beta is 2 The outlet flow angle for the splitter vane 2; q (Q) r Calculating flow for the design working point; a is that 2 In order to consider the actual axial surface flow water cross-sectional area on the circumference of the water outlet edge of the splitter blade 2 after the splitter blade 2 is added; u (u) 2 Is the peripheral velocity of the liquid at the outlet edge of the splitter vane 2; v m2 The absolute velocity at the outlet of the splitter vane 2 is the split velocity in the direction of the axial plane. By verifying the turbine by pumps with various different specific speeds, it was found that the negative outlet speed moment is advantageous for improving efficiency and operational stability, according to the outlet speed triangle of fig. 8, for example when the outlet speed moment of the splitter blades 2 is distributed according to-1% of the inlet speed moment of the blades, i.e. v u2 r 2 ＝-0.01v u1 r 1 Wherein the inlet velocity moment v u1 r 1 Through the already known technologyThe opening technology can be obtained through the geometric parameters of the volute, so that the absolute speed of the outlet of the splitter vane 2 in the circumferential direction can be obtained, and the absolute speed is as follows:
v u2 ＝-0.01v u1 r 1 /(D 2 /2)。 (5)
bringing the formula (5) into the formula (3) to obtain the calculation formula of the outlet liquid flow angle of the splitter blade 2, wherein the calculation formula is as follows:
preferably, in the third step, the calculation formula of the outlet setting angle of the splitter blade 2 is as follows:
β b2 ＝β 2 (4)
wherein beta is b2 The angle at which the splitter blade exits. Assuming that the streamline direction of the relative movement of the liquid outlet is consistent with the streamline direction of the outlet of the splitter blade, the outlet setting angle beta of the splitter blade b2 Angle beta of flow relative to outlet 2 Equality, i.e. taking beta without consideration of relative slippage of liquid in the turbine wheel b2 ＝β 2 。
Further optimization scheme, in equation 2
Wherein D is 2 The diameter of the water outlet edge of the splitter blade is related to the length of the splitter blade; n is the rotational speed of the impeller.
In a further optimization scheme, the inlet sweep angle of the splitter blade 2 is negative, and the value of the inlet sweep angle is-2 degrees to-6 degrees.
According to a further optimization scheme, the inlet thickness of the splitter blade 2 is larger than the outlet thickness, and the surface of the splitter blade 2 is smooth. The inlet thickness of the splitter blades 2 is greater than the outlet thickness because of the high pressure at the inlet of the impeller due to the strength. The thickness of the blade changes according to a linear rule; the splitter blades 2 are arranged smoothly from the inlet to the outlet, so that turbulence in the fluid and vortex motion in the flow channel are reduced, the resistance of the splitter blades 2 to the fluid can be reduced, the running stability of the fluid is improved, and the turbine power of the impeller is improved.
Further, the change rule of the setting angle of the splitter vane 2 may be a linear change rule, a cubic polynomial change rule or a penta polynomial change rule. Different laws determine different curved shapes in the middle of the blade. In the case of the same blade wrap angle, the linearity rule is best, as in the blade generated as shown in fig. 5 a.
In a further optimization scheme, the length of the main blade 1 is L, and the length of the splitter blade 2 is 0.5L-0.8L.
In a further optimization scheme, the included angle of the adjacent main blades 1 is theta, and the offset angle of the splitter blade 2 is 0.4-0.6 theta. θ is an included angle between two adjacent main blades 1, and is determined according to the number of the main blades 1, and if the number of the main blades 1 is Z, the value of θ is equal to 360/Z; the degree of offset of the splitter blade 2 reflects the position of the splitter blade 2 relative to the main blades 1, 0.5 theta indicating that the splitter blade 2 is located intermediate the two main blades 1, 0.4 theta indicating that the splitter blade 2 is located close to the suction surface, and 0.6 theta indicating that the splitter blade 2 is located close to the pressure surface.
According to the comparison of the conventional turbine wheel and the external characteristic curve of the present application in fig. 6-7, after the splitter blade 2 of the present application is added, the required water head of the turbine is reduced at the same flow, and the operation efficiency of the turbine is obviously improved from the high-efficiency point to the high-flow working condition.
Further, in fig. 4, a represents negative inlet sweep, b represents 0, and c represents positive inlet sweep.
Further, in fig. 5, a represents a linear change curve, B represents a cubic polynomial change curve, and C represents a penta polynomial change curve.
In the description of the present invention, it should be understood that the terms "longitudinal," "transverse," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like indicate or are based on the orientation or positional relationship shown in the drawings, merely to facilitate description of the present invention, and do not indicate or imply that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus should not be construed as limiting the present invention.
The above embodiments are only illustrative of the preferred embodiments of the present invention and are not intended to limit the scope of the present invention, and various modifications and improvements made by those skilled in the art to the technical solutions of the present invention should fall within the protection scope defined by the claims of the present invention without departing from the design spirit of the present invention.
Claims (8)
1. A method of designing a splitter vane for a hydraulic turbine, comprising the steps of:
step one: determining inlet setting angles of the main blades (1), forming a flow channel between adjacent main blades (1), wherein the inlet of the splitter blade (2) is consistent with the inlet setting angle of the main blade (1);
step two: determining the length and the offset angle of the splitter blade (2);
step three: determining the setting angle of the outlet of the splitter blade (2); the efficiency of the turbine when the velocity moment of the outlet is positive, zero and negative is calculated respectively, and then the setting angle of the outlet of the splitter blade (2) is determined;
step four: determining an inlet sweep angle of the splitter blade (2); calculating the efficiency of the turbine when the inlet sweep angle is positive, zero and negative respectively, thereby determining the inlet sweep angle;
step five: the inlet and the outlet of the splitter blade (2) are connected, so that the surface from the inlet to the outlet of the splitter blade (2) is smooth and continuous.
2. The method of designing a splitter vane for a hydraulic turbine of claim 1, wherein: in the third step, the outlet speed moment of the splitter blade (2) is negative, the outlet speed moment of the splitter blade (2) is-1% -4% of the inlet speed moment, at this time, the absolute speed of the outlet in the outlet speed triangle has a circumferential component speed opposite to the rotation direction of the impeller, and a liquid flow angle calculation formula at the outlet of the splitter blade can be obtained:
wherein,,
substituting the formula (2) into the formula (1) to obtain a calculation formula of the flow angle of the outlet of the splitter blade, wherein the calculation formula is as follows:
wherein beta is 2 For the flow angle of the outlet flow of the splitter blade (2); q (Q) r Calculating flow for the design working point; a is that 2 In order to consider the actual axial surface flow water cross-sectional area on the circumference of the water outlet edge of the splitter blade (2) after the splitter blade (2) is added; u (u) 2 Is the peripheral speed of the liquid at the outlet edge of the splitter blade (2); v m2 The absolute velocity at the outlet of the splitter vane is the split velocity in the direction of the axial plane.
3. The method of designing a splitter vane for a hydraulic turbine of claim 2, wherein: in the third step, the calculation formula of the outlet setting angle of the splitter blade (2) is as follows:
β b2 ＝β 2 (4)
wherein beta is b2 The outlet mounting angle of the splitter blade (2).
4. The method of designing a splitter vane for a hydraulic turbine of claim 2, wherein: in formula (2)
Wherein D is 2 For the splitter blade (2)The diameter of the water edge is related to the length of the splitter blade (2); n is the rotational speed of the impeller.
5. The method of designing a splitter vane for a hydraulic turbine of claim 1, wherein: the inlet sweep angle of the splitter blade (2) is negative and takes the value of-2 degrees to-6 degrees.
6. The method of designing a splitter vane for a hydraulic turbine of claim 1, wherein: the thickness of the inlet of the splitter blade (2) is larger than that of the outlet, and the surface of the splitter blade (2) is smooth.
7. The method of designing a splitter vane for a hydraulic turbine of claim 1, wherein: the length of the main blade (1) is L, and the length of the splitter blade (2) is 0.5L-0.8L.
8. The method of designing a splitter vane for a hydraulic turbine of claim 1, wherein: the included angle of the adjacent main blades (1) is theta, and the offset angle of the splitter blade (2) is 0.4 theta-0.6 theta.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN202310260715.XA CN116451364A (en) | 2023-03-17 | 2023-03-17 | Design method of hydraulic turbine impeller splitter blade |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202310260715.XA CN116451364A (en) | 2023-03-17 | 2023-03-17 | Design method of hydraulic turbine impeller splitter blade |
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