CN114278613B - Double-volute for efficient centrifugal pump and double-volute hydraulic design method for efficient centrifugal pump - Google Patents
Double-volute for efficient centrifugal pump and double-volute hydraulic design method for efficient centrifugal pump Download PDFInfo
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Abstract
The invention relates to a double volute for a high-efficiency centrifugal pump and a double volute hydraulic design method for the high-efficiency centrifugal pump, which solve the technical problem of balancing radial force on the premise of ensuring efficiency when the double volute is designed, accurately define the base circle diameter, the inlet width and the volute partition tongue placement angle of the double volute, define the starting position and the shape of a partition plate, and fulfill the aim of balancing radial force generated in the operation process of the pump to a certain extent under the premise of ensuring efficiency. The invention is widely applied to the technical field of design and manufacture of double-volute double-suction pumps.
Description
Technical Field
The invention relates to the technical field of design and manufacture of double-volute double-suction pumps, in particular to a double-volute for an efficient centrifugal pump and a double-volute hydraulic design method for the efficient centrifugal pump.
Background
During operation, the large-flow centrifugal pump generates radial force acting on the impeller, so that the shaft is subjected to alternating stress to generate directional deflection. The damage of the pump shaft and the damage of the sealing ring of the large double-suction pump are caused by overlarge radial force, so that the large-flow pump adopts a double-volute structure. As a high-efficiency centrifugal pump, the double-volute double-suction pump not only inherits the advantages of high lift, large flow, balanced axial force and the like of the single-volute double-suction centrifugal pump, but also can effectively reduce the radial force of the impeller generated in the operation process of the pump and improve the vibration condition of a pump station system. However, the radial force of the double volute pump is not fully studied at present, and the determination of the basic size of the double volute is still dependent on an empirical design method, and cannot be accurately defined according to basic parameters of the pump in the design process. And the double volutes balance radial force on the basis of loss efficiency, and the sacrifice efficiency does not meet the energy-saving and environment-friendly requirements advocated at present. Therefore, how to balance the radial force without sacrificing the efficiency index and guaranteeing the efficiency is a technical problem to be solved by the skilled person.
Disclosure of Invention
The invention provides a double volute for a high-efficiency centrifugal pump and a double volute hydraulic design method for the high-efficiency centrifugal pump, aiming at solving the technical problem of balancing radial force on the premise of ensuring efficiency when the double volute is designed.
The invention discloses a high-efficiency multi-working-condition double-volute hydraulic design method, which is used for accurately defining basic parameters of double volutes and defining the initial position and shape of a baffle plate, so that the purpose of balancing radial force generated in the operation process of a pump to the greatest extent on the premise of ensuring efficiency is achieved to a certain extent.
The invention provides a double-volute hydraulic design method for a high-efficiency centrifugal pump, which comprises the following steps of:
calculating the base circle diameter D of the double volute by the following formula 3 ：
In the above, D 3 The base circle diameter of the double volutes is expressed in meters; n is n s Representing the designed pump specific speed; q represents the design pump flow in meters 3 A/sec; h represents the design pump lift in meters; n represents the design pump speed in revolutions per minute;
by the following steps ofThe following formula calculates the double-volute inlet width b 3 ：
Double volute inlet width b 3 In the calculation formula of (2), n s Representing the designed pump specific speed; q represents the design pump flow in meters 3 A/sec; h represents the design pump lift in meters; n represents the design pump speed in revolutions per minute;
calculating volute tongue placement angle by the following formula
Volute tongue-separating mounting angleIn the calculation formula, n s Representing the designed pump specific speed; q represents the design pump flow in meters 3 A/sec; h represents the design pump lift in meters; n represents the design pump speed in revolutions per minute;
the position of the partition plate in the double-volute structure is determined according to the design pump lift, when the design pump lift is less than or equal to 80m, the initial position of the partition plate is positioned at the 7 th section and is ended at the 9 th section; when the pump lift is designed to be more than 80m, the initial position of the baffle plate is positioned at the 5 th section and is ended at the 9 th section.
Preferably, the starting position of the partition board adopts a V-shaped partition board design with the thickness gradually decreasing from two ends to the middle, and the ending position of the partition board adopts a V-shaped partition board design with the thickness gradually decreasing from two ends to the middle.
The invention also provides a double volute for the efficient centrifugal pump, and the base circle diameter D of the double volute 3 Calculated by the following formula:
in the above, D 3 The base circle diameter of the double volutes is expressed in meters; n is n s Representing the designed pump specific speed; q represents the design pump flow in meters 3 A/sec; h represents the design pump lift in meters; n represents the design pump speed in revolutions per minute;
inlet width b of double volute 3 Calculated by the following formula:
double volute inlet width b 3 In the calculation formula of (2), n s Representing the designed pump specific speed; q represents the design pump flow in meters 3 A/sec; h represents the design pump lift in meters; n represents the design pump speed in revolutions per minute;
volute tongue-separating mounting angle of double volutesCalculated by the following formula:
volute tongue-separating mounting angleIn the calculation formula, n s Representing the designed pump specific speed; q represents the design pump flow in meters 3 A/sec; h represents the design pump lift in meters; n represents the design pump speed in revolutions per minute;
the position of the partition plate in the double-volute structure is determined according to the design pump lift, when the design pump lift is less than or equal to 80m, the initial position of the partition plate is positioned at the 7 th section and is ended at the 9 th section; when the pump lift is designed to be more than 80m, the initial position of the baffle plate is positioned at the 5 th section and is ended at the 9 th section.
Preferably, the starting position of the partition board adopts a V-shaped partition board design with the thickness gradually decreasing from two ends to the middle, and the ending position of the partition board adopts a V-shaped partition board design with the thickness gradually decreasing from two ends to the middle.
The invention has the beneficial effects that a totally new double-volute hydraulic design method for the high-efficiency centrifugal pump is disclosed, and radial force generated in the operation process of the pump is balanced to the greatest extent on the premise of ensuring the efficiency.
Further features and aspects of the present invention will become apparent from the following description of specific embodiments with reference to the accompanying drawings.
Drawings
Fig. 1 is a double volute hydrograph.
FIG. 2 is a partial view of the direction A of FIG. 1;
FIG. 3 is a partial view of the direction D of FIG. 2;
FIG. 4 is an interface of a CFD software simulation analysis flow channel.
Description of the symbols in the drawings: the partial view in the direction B in fig. 1 is the same as fig. 2, and the partial view in the direction C in fig. 1 is the same as fig. 2. 20. Impeller, 30, inlet extension, 40, outlet extension, 50, suction chamber, 60, extrusion chamber.
Detailed Description
The double-volute hydraulic structure comprises a spiral section, a diffusion section and a partition plate. The invention discloses a high-efficiency multi-working-condition double-volute hydraulic design method, which is characterized in that basic parameters of a double volute are precisely defined, and the initial position and the shape of a baffle are defined, so that the double-volute structure is improved, and the radial force generated in the operation process of a pump is balanced to the greatest extent on the premise of ensuring the efficiency.
Calculating the base circle diameter D of the double volute by the following formula 3 ：
In the above, D 3 The base circle diameter of the double volutes is expressed in meters; n is n s Representing the designed pump specific speed; q represents the design pump flow in meters 3 A/sec; h represents the design pump lift in meters; n represents the design pump speed in revolutions per minute.
The double volute inlet width b is calculated by the following formula 3 ：
In the above, b 3 Represents the width of the inlet of the double volute, and the unit is meter; n is n s Representing the designed pump specific speed; q represents the design pump flow in meters 3 A/sec; h represents the design pump lift in meters; n represents the design pump speed in revolutions per minute.
Calculating volute tongue placement angle by the following formula
In the above-mentioned method, the step of,the volute tongue-separating setting angle is expressed, and the unit is degree; n is n s Representing the designed pump specific speed; q represents the design pump flow in meters 3 A/sec; h represents the design pump lift in meters; n represents the design pump speed in revolutions per minute.
The partition plates in the double volute structure are important factors causing efficiency loss of the centrifugal pump, and the arrangement and the shape of the partition plates are improved in order to reduce the efficiency loss. The 1 st section, 2 nd section, 3 rd section, 4 th section, 5 th section, 6 th section, 7 th section, 8 th section, 9 th section, 10 th section and 11 th section in the twin-volute structure are determined by a conventional method. The initial position of the baffle is changed according to the difference of the design pump lift, referring to fig. 1, when the design pump lift is less than or equal to 80m, the initial position of the baffle is positioned at the 7 th section and ends at the 9 th section; when the pump lift is designed to be more than 80m, the initial position of the baffle plate is positioned at the 5 th section and is ended at the 9 th section. As shown in fig. 2, the starting position of the separator adopts a V-shaped separator design, and the thickness of the V-shaped separator design gradually decreases from both ends to the middle, as shown in fig. 3. The end position of the baffle plate is designed by adopting a V-shaped baffle plate, and the thickness of the V-shaped baffle plate is gradually decreased from two ends to the middle.
Thus, the design of the double spiral case for the centrifugal pump is completed.
The performance of the double volutes formed by the double volute hydraulic design method of the invention and the double volutes and the single volutes formed by the traditional design method in terms of efficiency and radial force are compared through simulation experiments. Simulation experiments are carried out through CFD software, and the basic parameters of numerical simulation are that the flow Q=800 m 3 and/H, lift H=56m, rotation speed n=1480r/min, specific rotation speed n s ＝88(80≤n s 160), the blades on two sides are symmetrically arranged back to back, and the extrusion chamber is a single volute mechanism; the whole flow channel is divided into 5 parts, namely an impeller, a suction chamber, an extrusion chamber, an inlet extension section and an outlet extension section, and grid division is carried out by adopting a grid division module of CFD software; when the pressure is calculated, the environmental reference pressure is a standard atmospheric pressure, the boundary condition adopts a total pressure inlet and a mass flow outlet, the total inlet pressure is 1bar, and the turbulence model adopts a k-epsilon model. The hydraulic power of the suction chamber and the impeller is unchanged, and the hydraulic design of the extrusion chamber is only changed, so that the calculation results are shown in the table 1 below.
Table 1:
| category(s) | Efficiency of | Impeller outlet radial force |
| Single worm formed by traditional design methodShell and shell | 87.5％ | X：368N Y：668N |
| Double volute formed by traditional design method | 86.3％ | X：-168N Y：-78N |
| The double spiral case formed by the design method of the invention | 87.1％ | X：-268N Y：-99N |
Remarks: the traditional design method is a design method related to textbooks of modern pump theory and design.
As can be seen from the calculation results in table 1, compared with the single volute, the efficiency of 87.1% is slightly less than 87.5%, the radial force is greatly reduced, and the radial force is balanced under the condition that the efficiency requirement is met. Compared with a single volute, the radial force of the double volute formed by the traditional design is greatly reduced, but the efficiency is reduced by 1.2%, and the efficiency is more reduced.
The above description is only for the preferred embodiments of the present invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art.
Claims (4)
1. The double-volute hydraulic design method for the efficient centrifugal pump is characterized by comprising the following steps of:
calculating the base circle diameter D of the double volute by the following formula 3 ：
In the above, D 3 Representing double snailsThe base circle diameter of the shell in meters; n is n s Representing the designed pump specific speed; q represents the design pump flow in meters 3 A/sec; h represents the design pump lift in meters; n represents the design pump speed in revolutions per minute;
the double volute inlet width b is calculated by the following formula 3 ：
The inlet width b of the double volute 3 In the calculation formula of (2), n s Representing the designed pump specific speed; q represents the design pump flow in meters 3 A/sec; h represents the design pump lift in meters; n represents the design pump speed in revolutions per minute;
calculating volute tongue placement angle by the following formula
The volute tongue-separating mounting angleIn the calculation formula, n s Representing the designed pump specific speed; q represents the design pump flow in meters 3 A/sec; h represents the design pump lift in meters;
the position of the partition plate in the double-volute structure is determined according to the design pump lift, when the design pump lift is less than or equal to 80m, the initial position of the partition plate is positioned at the 7 th section and is ended at the 9 th section; when the pump lift is designed to be more than 80m, the initial position of the baffle plate is positioned at the 5 th section and is ended at the 9 th section.
2. The method for designing double-volute hydraulic power for a high-efficiency centrifugal pump according to claim 1, wherein the starting position of the partition plate is designed by adopting a V-shaped partition plate with the thickness gradually decreasing from two ends to the middle, and the ending position of the partition plate is designed by adopting a V-shaped partition plate with the thickness gradually decreasing from two ends to the middle.
3. A double volute for a high-efficiency centrifugal pump is characterized in that the base circle diameter D of the double volute 3 Calculated by the following formula:
in the above, D 3 The base circle diameter of the double volutes is expressed in meters; n is n s Representing the designed pump specific speed; q represents the design pump flow in meters 3 A/sec; h represents the design pump lift in meters; n represents the design pump speed in revolutions per minute;
inlet width b of the double volute 3 Calculated by the following formula:
the inlet width b of the double volute 3 In the calculation formula of (2), n s Representing the designed pump specific speed; q represents the design pump flow in meters 3 A/sec; h represents the design pump lift in meters; n represents the design pump speed in revolutions per minute;
volute tongue-separating mounting angle of double volutesCalculated by the following formula:
the volute tongue-separating mounting angleIn the calculation formula, n s Representing the designed pump specific speed; q represents the design pump flow in meters 3 A/sec; h represents the design pump lift in meters;
the position of the partition plate in the double-volute structure is determined according to the design pump lift, when the design pump lift is less than or equal to 80m, the initial position of the partition plate is positioned at the 7 th section and is ended at the 9 th section; when the pump lift is designed to be more than 80m, the initial position of the baffle plate is positioned at the 5 th section and is ended at the 9 th section.
4. A twin scroll for a high efficiency centrifugal pump according to claim 3, wherein the start position of the partition is designed as a V-shaped partition having a thickness gradually decreasing from both ends to the middle, and the end position of the partition is designed as a V-shaped partition having a thickness gradually decreasing from both ends to the middle.
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| CN102032217A (en) * | 2010-12-27 | 2011-04-27 | 中国农业大学 | Method for optimizing dummy plate of double-volute type double-suction pump and product produced with same |
| CN105221485A (en) * | 2015-10-16 | 2016-01-06 | 江苏大学 | A kind of low specific speed centrifugal pump spiral pressurized water chamber Hydraulic Design Method |
| CN205639074U (en) * | 2016-03-30 | 2016-10-12 | 上海东方泵业(集团)有限公司 | Pump body spiral case structure |
| CN106934177A (en) * | 2017-04-01 | 2017-07-07 | 江苏大学镇江流体工程装备技术研究院 | A kind of Optimization Design of double volute mixed-flow pump dividing plate |
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| EP2182220A1 (en) * | 2008-10-28 | 2010-05-05 | Nederlandse Organisatie voor toegepast-natuurwetenschappelijk Onderzoek TNO | Turbo machine and method to reduce vibration in turbo machines. |
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Patent Citations (4)
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|---|---|---|---|---|
| CN102032217A (en) * | 2010-12-27 | 2011-04-27 | 中国农业大学 | Method for optimizing dummy plate of double-volute type double-suction pump and product produced with same |
| CN105221485A (en) * | 2015-10-16 | 2016-01-06 | 江苏大学 | A kind of low specific speed centrifugal pump spiral pressurized water chamber Hydraulic Design Method |
| CN205639074U (en) * | 2016-03-30 | 2016-10-12 | 上海东方泵业(集团)有限公司 | Pump body spiral case structure |
| CN106934177A (en) * | 2017-04-01 | 2017-07-07 | 江苏大学镇江流体工程装备技术研究院 | A kind of Optimization Design of double volute mixed-flow pump dividing plate |
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| 双蜗壳泵隔板长度对径向力平衡的影响;施瀚昱;牟介刚;郑水华;甘建军;林玲;范文粲;;浙江农业学报(06);全文 * |
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