CN114151379A - Hydraulic model of high-efficiency chemical centrifugal pump - Google Patents
Hydraulic model of high-efficiency chemical centrifugal pump Download PDFInfo
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2205—Conventional flow pattern
- F04D29/2222—Construction and assembly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
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- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
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- F04D29/24—Vanes
- F04D29/242—Geometry, shape
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
- F04D29/428—Discharge tongues
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps
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Abstract
The invention relates to the technical field of pump design and manufacture, and provides a hydraulic model of a high-efficiency chemical centrifugal pump, which comprises a pump body, an impeller, a pump cover, a pump body port ring and a pump cover port ring, wherein the impeller is a radial impeller, a front cover plate and a rear cover plate are arranged on two sides of the impeller, a meridian line of an impeller flow channel consists of a Bezier curve controlled by five points, the Bezier curve is rotated by 360 degrees and thickened by 6-7 mm to generate the front cover plate and the rear cover plate, 6 blades are uniformly and fixedly arranged on the circumference between the front cover plate and the rear cover plate, the impeller is positioned in the pump body, the center of the flow channel of the impeller is superposed with the center of the flow channel of the pump body, the port ring of the front cover plate of the impeller is in clearance fit with the port ring of the pump body, and the port ring of the rear cover plate of the impeller is in clearance fit with the port ring of the pump cover ring; according to the invention, hydraulic optimization design is carried out under the similar working condition that the comparison revolution number is ns =110, the flow rate is Q =270m3/H, the lift H is 32m, and the revolution number n is 1478, so that the hydraulic performance, the operating efficiency and the operating stability are improved.
Description
Technical Field
The invention relates to the technical field of pump design and manufacture, in particular to a hydraulic model of a high-efficiency chemical centrifugal pump.
Background
A chemical plant may have hundreds of pumping systems, and the motors driving the pumping systems consume large amounts of power. The pump accounts for 10% of the world's total electrical energy consumption. Centrifugal pumps are the most widely used pump type in the pump industry, and the usage amount of the centrifugal pumps accounts for about 70% of the whole pump industry. The pump is relatively large under the similar working condition that the specific revolution number is ns =110, the flow rate is Q =270m3/H, the head H is 32m, and the revolution number n is 1478, but the working efficiency of the pump is only 70% -75%, and the energy waste is relatively large. Therefore, the hydraulic optimization design of the original pump under the working condition has great significance.
For the hydraulic design of centrifugal pumps, it is mainly necessary to improve efficiency, performance and operational stability of the pump. The impeller is the most main overflowing part and acting part in the centrifugal pump, and the design advantages and disadvantages of the impeller directly influence the operating efficiency and the operating stability of the pump, and further influence the design targets of vibration, noise and the like of the pump, so that the hydraulic model mainly redesigns the impeller of the pump, and improves the hydraulic performance, the operating efficiency and the operating stability.
Disclosure of Invention
Solves the technical problem
Aiming at the defects of the prior art, the invention provides a hydraulic model of a high-efficiency chemical centrifugal pump, which is characterized in that hydraulic optimization design is carried out under the similar working condition that the contrast revolution number is ns =110, the flow rate is Q =270m3/H, the lift H is 32m, and the revolution number n is 1478, so that the hydraulic performance, the operating efficiency and the operating stability are improved.
Technical scheme
In order to achieve the purpose, the invention is realized by the following technical scheme:
a hydraulic model of a high-efficiency chemical centrifugal pump comprises a pump body, an impeller, a pump cover, a pump body port ring and a pump cover port ring, wherein the impeller is a radial-flow impeller, a front cover plate and a rear cover plate are arranged on two sides of the impeller, an impeller flow channel meridian line consists of a Bezier curve controlled by five points, the Bezier curve is generated into the front cover plate and the rear cover plate by rotating 360 degrees and thickening 6-7 mm, 6 blades are uniformly and fixedly arranged on the circumference between the front cover plate and the rear cover plate, the impeller is positioned in the pump body, the center of a flow channel of the impeller is superposed with the center of the flow channel of the pump body, the port ring of the front cover plate of the impeller is in clearance fit with the pump body port ring, the port ring of the rear cover plate of the impeller is in clearance fit with the pump cover port ring, and the clearance is 0.5 mm; wherein, the parameters of the hydraulic model are as follows: specific revolution ns =110, flow Q =270m3/H, head H equals 32m, revolution n equals 1478, and efficiency η is equal to or greater than 80%.
Further, the blade is a free 3D curved surface, and the thickness of the blade is 7 mm.
Further, the leading edge of the blade inlet is R1 round angle, and the blade is linearly thickened to the blade thickness of 7mm after passing through the length of 45 mm.
Furthermore, the curved surface of the blade comprises 5 flow lines which are respectively a front cover plate flow line, a rear cover plate flow line, a middle flow line, a central line of the front cover plate and the middle flow line and a central line of the rear cover plate and the middle flow line; the entry angle of the streamlines is β 1=20.9 ° -42.7 ° and increases linearly, the blade exit angle β 2=25.5 °, and the blade wrap angle ψ =130 °.
Furthermore, the inlet diameter of the impeller is 160mm, and the specific calculation process is as follows:
D0=K0=4.3=4.3 × 0.037=0.16 m; wherein:
d0-impeller inlet diameter, m; q is the flow rate of the pump, m 3/s; n-impeller speed, rpm; k0 — coefficient.
Furthermore, the diameter of the shaft hole of the impeller is 42mm, and the specific calculation process is as follows:
(1) shaft power P = = =28.71kw
(2) Motor power PC= P = × 28.71=33kw wherein:
k is the motor margin coefficient, and the motor margin coefficient K =1.15 is found out when 28kw is obtained;
transmission efficiency factor, transmission efficiency =1 due to direct motor drive
(3) Torque =9550k =9550 × 1.1 × 33 ÷ 1478=234N ∙ m; wherein:
k-safety factor, K = 1.1;
(4) impeller shaft hole diameter d = =0.042 m; wherein:
allowable shear stress, when 3Cr13 is selected as the material, is not less than 15 MPa. .
Furthermore, the outer diameter of the impeller is 330mm, and the specific calculation process is as follows:
KD2=9.35()-1/2=8.91
D2= KD28.91 =0.33 m; wherein:
d2 — mean impeller exit diameter; q is the flow rate of the pump, m 3/s; n-impeller speed, rpm;
n s-Pump specific number of revolutions.
Furthermore, the outlet width of the impeller is 30mm, and the specific calculation process is as follows:
Kb2=0.64（）5/6=0.693
b2= Kb Kb2=1.15 × 0.693 × =0.0295 ≈ 0.03 m; wherein:
b 2-mean width of impeller exit; q is the flow rate of the pump, m 3/s; n-impeller speed, rpm;
n s-Pump specific revolutions; kb — correction factor, Kb = 1.15.
Furthermore, the pump body is a variable-section spiral annular pumping chamber, the base circle of the pumping chamber is 340mm, the cross-sectional area of the maximum flow cross section of a volute chamber in the pump body is 4957.3mm2, the length of a diffusion section of the volute chamber is 200mm, the mounting angle of a volute tongue is 22, the diameter of an inlet of the pump body is 150mm, the diameter of an outlet of the pump body is 125mm, and the center of the pump body is 355mm from the center to the plane of the outlet.
According to the design parameters of the original chemical centrifugal pump, the calculation domain of the pump body water body and the impeller water body is quickly modeled by taking efficiency and hydraulic performance as objective functions and by using a CF turbo software built-in empirical function and a speed triangle theory based on a genetic algorithm. And performing numerical simulation on the whole machine at 75-125% rated flow by virtue of Fluent software to obtain hydraulic performance and efficiency, obtaining a hydraulic performance curve and a cavitation performance curve of the hydraulic model of the chemical centrifugal pump under the whole working condition, and performing modeling and numerical simulation for multiple times to obtain an optimal hydraulic model meeting design requirements. And leading the optimal hydraulic model into Solid Works to draw a three-dimensional model. Impeller precision casting is with disappearing wax model and prints quick shaping through 3D.
Advantageous effects
The invention provides a hydraulic model of a high-efficiency chemical centrifugal pump, which has the following beneficial effects compared with the prior art:
1. the hydraulic model of the invention has higher hydraulic efficiency by optimally designing the impeller main body of the centrifugal pump and the assembly details of the impeller main body and the pump body, and the efficiency can only reach 70% -75% at most compared with the pump body in the prior art, while the efficiency of the high-efficiency chemical centrifugal pump hydraulic model of the invention reaches 82%; thereby effectively reducing power consumption and saving energy and unit operation cost.
And the weight and the volume of the centrifugal pump under the working condition are reduced by about 15 percent compared with the original model, thereby greatly saving the manufacturing cost and improving the enterprise benefit. The design method of the invention carries out three-dimensional modeling, flow field numerical simulation and theoretical analysis on the basis of hydraulic model design combining traditional theory and modern theory, and then carries out multiple geometric dimension correction matching to obtain the hydraulic model with excellent performance. The whole product research and development period can be greatly shortened, and the time and the labor cost are saved. The centrifugal pump unit optimized by the process has high operation efficiency, wide working condition range and good cavitation resistance, and can work stably for a long time under all working conditions.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
FIG. 1 is a front and rear perspective view of an impeller of the present invention;
FIG. 2 is a schematic view of a linear planar projection of a blade according to the present invention;
FIG. 3 is a schematic view of the assembly of three-dimensional pump body parts of the chemical centrifugal pump according to the present invention;
FIG. 4 is a cross-sectional axial view of an impeller of a chemical centrifugal pump according to the present invention;
FIG. 5 is a schematic view of a pump body component of the present invention;
FIG. 6 is a schematic diagram of the velocity distribution of the flow field in the chemical centrifugal pump according to the present invention;
FIG. 7 is a schematic diagram of the pressure distribution of the flow field in the chemical centrifugal pump according to the present invention;
FIG. 8 is a graph of performance of a prior art prototype pump;
FIG. 9 is a graph of the performance of the centrifugal pump of the present invention;
the reference numerals in the drawings denote: 1-pump body, 2-pump cover, 3-impeller, 4-pump cover opening ring, 5-pump body opening ring, 6-pump shaft, 7-anti-reverse screw, 8-bearing frame, 9-mechanical seal, 10-shaft sleeve, 11-bearing gland, 12-dustproof disc, 13-sealing gland, 14-cylindrical roller bearing, 15-angular contact ball bearing, 16-bearing locking nut, 301-front cover plate, 302-blade, 303-flow guide surface, 304-rear cover plate and 305-hub.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, 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 some, but not all, embodiments of the present invention. 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.
Example (b):
the hydraulic model of the high-efficiency chemical centrifugal pump comprises a pump body 1, an impeller 3, a pump cover 2, a pump body port ring 5 and a pump cover port ring 4, wherein the impeller 3 is a radial-flow impeller 3, a front cover plate 301 and a rear cover plate 304 are arranged on two sides of the impeller 3, a meridian line of a flow channel of the impeller 3 is formed by a Bezier curve controlled by five points, the Bezier curve is rotated for 360 degrees and thickened for 6-7 mm to generate the front cover plate 301 and the rear cover plate 304, 6 blades 302 are uniformly and fixedly arranged on the circumference between the front cover plate 301 and the rear cover plate 304, the impeller 3 is positioned in the pump body 1, the center of the flow channel of the impeller 3 is superposed with the center of the flow channel of the pump body 1, the port ring of the front cover plate 301 of the impeller 3 is in clearance fit with the pump body port ring 5, the port ring of the rear cover plate 304 of the impeller 3 is in clearance fit with the pump cover port ring 4, and the clearances are both 0.5 mm; wherein, the parameters of the hydraulic model are as follows: specific revolution ns =110, flow Q =270m3/H, head H equals 32m, revolution n equals 1478, and efficiency η is equal to or greater than 80%.
Referring to fig. 3, the hydraulic model main body in this embodiment includes a pump body 1, an impeller 3, a pump cover 2, a pump body port ring 5, a pump cover port ring 4, a pump shaft 6, and other components, and the assembling manner therebetween is the same as that of the centrifugal pump body 1 in the prior art, and specifically: the cylindrical roller bearing 14 and the back-to-back paired angular contact ball bearings 15 are heated and installed at the front and back bearing positions of the pump shaft 6, the back-to-back paired angular contact ball bearings 15 are fixed through the bearing locking nuts 16, the assembled pump shaft 6 part is installed in the bearing frame 8, the bearing gland 11 and the dustproof disc 12 are installed at two sides of the bearing frame 8 through bolts, the static ring of the mechanical seal 9 is respectively installed on the pump cover 2 and the sealing gland 13, the dynamic ring of the mechanical seal 9 is installed on the shaft sleeve 10 after measuring the size, the mechanical seal 9 and the shaft sleeve 10 are installed in a sealing cavity formed by connecting the pump cover 2 and the sealing gland 13 through bolts, the pump cover mouth ring 4 is installed in the pump cover 2 through bolts, the pump body mouth ring 5 is installed in the pump body 1 through bolts, the pump shaft 6 and the impeller 3 are connected through threads and fastened through the anti-reverse rotation bolts 7, and the pump cover 2 and the pump body 1 are connected on the bearing frame 8 through bolts, the impeller 3 is positioned in the pump body 1, the center of a flow channel of the impeller 3 is superposed with the center of a flow channel of the pump body 1, the opening ring of a front cover plate 301 of the impeller 3 is in clearance fit with the opening ring of the pump body 5, the opening ring of a rear cover plate 304 of the impeller 3 is in clearance fit with the opening ring of the pump cover 4, the clearance is 0.5mm, and the bearing frame 8 and the pump body 1 are fixed on a pump base through bolts.
Referring to fig. 5, the pump body 1 of the present embodiment is a variable cross-section spiral annular pumping chamber, the base circle of the pumping chamber is 340mm, the cross-sectional area of the maximum flow cross-section of the volute inside the pump body 1 is 4957.3mm2, the diffusion section length of the volute is 200mm, the volute installation angle is 22, the inlet diameter of the pump body 1 is 150mm, the outlet diameter of the pump body 1 is 125mm, and the center of the pump body 1 is 355mm from the outlet plane.
Referring to fig. 1, the impeller 3 is composed of a front shroud 301, blades 302, a guide surface 303, a rear shroud 304, and a hub 305. In this embodiment, the number of blades 302 is 6, the blades 302 are free 3D curved surfaces, and the thickness of the blades 302 is 7 mm. The leading edge of the inlet of the blade 302 is R1 round angle, and the blade 302 is linearly thickened to the thickness of the blade 302 of 7mm after passing through the length of 45 mm.
Referring to the linear planar projection diagram of the blade 302 shown in fig. 2, the curved surface of the blade 302 includes 5 streamlines, which are respectively a front cover plate 301 streamline, a rear cover plate 304 streamline, an intermediate streamline, a central line between the front cover plate 301 and the intermediate streamline, and a central line between the rear cover plate 304 and the intermediate streamline; the inlet angle of the streamlines is β 1=20.9 ° -42.7 ° and increases linearly, the blade 302 outlet angle β 2=25.5 °, and the blade 302 wrap angle ψ =130 °. The flow channel meridian lines of the front cover plate 301 and the rear cover plate 304 are obtained by adjusting five points of two bezier curves of the flow channel meridian plane. When two Bezier curves are adjusted, the meridian curvature curve in the CF turbo does not have a large wave crest, the meridian flow velocity curve does not have a local radius of 0, the cross-sectional area curve does not have a local maximum value or minimum value, and the static moment curves of the outlets of the front cover plate 304 and the rear cover plate 304 are approximately equal, and when the five curves are met, the optimal meridian of the flow channel of the front cover plate 304 and the rear cover plate 304 can be obtained.
Referring to fig. 4, which shows a cross-sectional view of the axial plane of the impeller 3 and fig. 2, the diameter of the inlet of the impeller 3 is 160mm, and the specific calculation process is as follows:
D0=K0=4.3=4.3 × 0.037=0.16 m; wherein:
d0-diameter of inlet of impeller 3, m; q is the flow rate of the pump, m 3/s; n-the rotational speed of the impeller 3, rpm; k0 — coefficient. Wherein, K0 is 4-5; if the efficiency is mainly considered, the value is 3.5-4.0; if the efficiency and the cavitation are considered, the ratio is 4.0-4.5; if cavitation is mainly considered, the amount is 4.5-5.0. The pump hydraulic orientation K0 is considered together to be 4.3.
The diameter of the shaft hole of the impeller 3 is 42mm, and the specific calculation process is as follows:
(1) shaft power P = = =28.71kw
(2) Motor power PC= P = × 28.71=33kw wherein:
k is the motor margin coefficient, and the motor margin coefficient K =1.15 is found out when 28kw is obtained;
transmission efficiency factor, transmission efficiency =1 due to direct motor drive
(3) Torque =9550k =9550 × 1.1 × 33 ÷ 1478=234N ∙ m; wherein:
k-safety factor, K = 1.1;
(4) the diameter d = = =0.042m of the shaft hole of the impeller 3; wherein:
allowable shear stress, when 3Cr13 is selected as the material, is not less than 15 MPa.
The outer diameter of the impeller 3 is 330mm, and the specific calculation process is as follows:
KD2=9.35()-1/2=8.91
D2= KD28.91 =0.33 m; wherein:
d2 — mean diameter of exit of impeller 3; q is the flow rate of the pump, m 3/s; n-the rotational speed of the impeller 3, rpm;
n s-Pump specific number of revolutions.
The outlet width of the impeller 3 is 30mm, and the specific calculation process is as follows:
Kb2=0.64（）5/6=0.693
b2= Kb Kb2=1.15 × 0.693 × =0.0295 ≈ 0.03 m; wherein:
b 2-average width of the exit of the impeller 3; q is the flow rate of the pump, m 3/s; n-the rotational speed of the impeller 3, rpm;
n s-Pump specific revolutions; kb — correction factor, Kb = 1.15.
According to the design parameters of the original chemical centrifugal pump, the water body calculation domains of the pump body 1 and the impeller 3 are quickly modeled by taking efficiency and hydraulic performance as objective functions and by using a CF turbo software built-in empirical function and a speed triangle theory based on a genetic algorithm. And performing numerical simulation on the whole machine at 75-125% rated flow by virtue of Fluent software to obtain hydraulic performance and efficiency, obtaining a hydraulic performance curve and a cavitation performance curve of the hydraulic model of the chemical centrifugal pump under the whole working condition, and performing modeling and numerical simulation for multiple times to obtain an optimal hydraulic model meeting design requirements. And leading the optimal hydraulic model into Solid Works to draw a three-dimensional model. Impeller 3 precision casting is with disappearing wax model and is printed rapid prototyping through 3D.
After obtaining the optimized specific numerical value of the impeller 3, quickly modeling the water body of the pump body 1 and the water body calculation domain of the impeller 3 by taking efficiency and hydraulic performance as target functions through a CF turbo software built-in empirical function and a speed triangle theory based on a genetic algorithm, and carrying out overall numerical simulation of 75% -125% rated flow by using CFD numerical simulation software Fluent to obtain hydraulic performance and efficiency, so as to obtain an overall full-working-condition hydraulic performance curve and a cavitation performance curve of a hydraulic model of the chemical centrifugal pump, and obtaining an optimal hydraulic model meeting design requirements through multiple modeling and numerical simulation.
As shown in fig. 6, by comparing the velocity distribution of the flow field in the pump, the velocity distribution of the flow field in the pump is relatively uniform at the designed operating point. No flow rate points that are too high or too low exist.
Referring to fig. 7, for the pressure distribution of the flow field in the pump, the pressure of the flow field in the pump at the designed operating point gradually increases from the inlet of the impeller 3 to the outlet of the impeller 3, and the pressure distribution among the blades 302 is relatively uniform. No excessively high or low pressure points exist.
And (3) obtaining an optimal hydraulic model through numerical simulation of Fluent software, guiding the hydraulic model into SolidWorks to be matched with the pump body 1 and the pump cover 2 for drawing a three-dimensional model, and finally obtaining a three-dimensional model diagram. In the actual production and manufacture of the impeller 3, because a certain shrinkage ratio exists during casting, the proportion of the three-dimensional model diagram is enlarged by 2%, and a lost wax model of the impeller 3 is obtained by preferably rapid forming through 3D printing and then integral precision casting is carried out.
FIG. 8 is a graph of performance of a prototype pump of the prior art; wherein the abscissa is the flow, the ordinate is the lift, and the efficiency is marked on the curve. The performance curve of the prototype pump is obtained by a test workshop performance test, the test medium is normal temperature water and is at a rated rotating speed of 1478 rpm;
1. the flow rate is Q =200m3/H, the head H is 31m, and the efficiency eta = 79%.
2. The flow rate is Q =250m3/H, the head H =27 m, and the efficiency η = 73%.
3. The flow rate is Q =270m3/H, the head H is 25m, and the efficiency eta = 67%.
From the curve, the prototype pump can not reach the operating point required by the EQ125-33 hydraulic model, if the operating point is required to be reached, a centrifugal pump EK150-315 with one model larger is required to be selected, and the weight and the manufacturing cost of the prototype pump are higher than those of the prototype pump by more than 15%.
FIG. 9 is a performance curve of a chemical centrifugal pump according to the present invention; wherein the abscissa is the flow, the ordinate is the lift, and the efficiency is marked on the curve. The accurate performance curve of the hydraulic model is obtained by a test workshop performance test, the test medium is normal temperature water and is at a rated rotating speed of 1478 rpm;
1. the flow rate is Q =200m3/H, the head H is 37m, and the efficiency eta = 80%.
2. The flow rate is Q =250m3/H, the head H is 35m, and the efficiency eta = 82%.
3. The flow rate is Q =270m3/H, the head H is 33m, and the efficiency eta = 80%.
From the curve, the EQ125-33 hydraulic model can meet the working condition requirement, the working condition point of large flow is improved by more than 20% compared with the pump head of the prototype pump, and the efficiency is improved by about 10%.
The embodiment result shows that the high-efficiency hydraulic model pump designed according to the required parameters has higher operating efficiency, wider working condition range and better cavitation resistance, and can greatly reduce the energy consumption and spare part loss of enterprises. And the weight and the volume of the centrifugal pump under the working condition are reduced by about 15 percent compared with the original model, thereby greatly saving the manufacturing cost and improving the enterprise benefit. Therefore, the method has important significance and wide application prospect.
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. Without further limitation, an element defined by the phrase "comprising an … …" does not exclude the presence of other identical elements in a process, method, article, or apparatus that comprises the element.
The above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions of the embodiments of the present invention.
Claims (9)
1. A hydraulic model of a high-efficiency chemical centrifugal pump comprises a pump body, an impeller, a pump cover, a pump body port ring and a pump cover port ring, and is characterized in that the impeller is a radial-flow impeller, a front cover plate and a rear cover plate are arranged on two sides of the impeller, an impeller flow channel meridian line is composed of a Bezier curve controlled by five points, the Bezier curve is generated into the front cover plate and the rear cover plate by rotating 360 degrees and thickening 6-7 mm, 6 blades are uniformly and fixedly arranged on the circumference between the front cover plate and the rear cover plate, the impeller is positioned in the pump body, the center of the flow channel of the impeller coincides with the center of the flow channel of the pump body, the port ring of the front cover plate of the impeller is in clearance fit with the pump body port ring, the port ring of the rear cover plate of the impeller is in clearance fit with the pump cover port ring, and the clearance is 0.5 mm; wherein, the parameters of the hydraulic model are as follows: specific revolution ns =110, flow Q =270m3/H, head H equals 32m, revolution n equals 1478, and efficiency η is equal to or greater than 80%.
2. The hydraulic model of a high-efficiency chemical centrifugal pump according to claim 1, wherein the blades are free 3D curved surfaces, and the thickness of the blades is 7 mm.
3. The hydraulic model of a high efficiency chemical centrifugal pump of claim 2, wherein the leading edge of the vane inlet is R1 rounded corner, and the vane is linearly thickened to a vane thickness of 7mm over a length of 45 mm.
4. The hydraulic model of a high efficiency chemical centrifugal pump of claim 2, wherein the curved surface of the blade comprises 5 streamlines, the streamlines are respectively a front cover plate streamline, a rear cover plate streamline, an intermediate streamline, a centerline of the front cover plate and the intermediate streamline, and a centerline of the rear cover plate and the intermediate streamline; the entry angle of the streamlines is β 1=20.9 ° -42.7 ° and increases linearly, the blade exit angle β 2=25.5 °, and the blade wrap angle ψ =130 °.
5. The hydraulic model of a high-efficiency chemical centrifugal pump according to claim 1, wherein the diameter of the inlet of the impeller is 160mm, and the specific calculation process is as follows:
D0=K0=4.3=4.3 × 0.037=0.16 m; wherein:
d0-impeller inlet diameter, m;
q is the flow rate of the pump, m 3/s;
n-impeller speed, rpm;
k0 — coefficient.
6. The hydraulic model of a high-efficiency chemical centrifugal pump according to claim 1, wherein the diameter of the shaft hole of the impeller is 42mm, and the specific calculation process is as follows:
(1) shaft power P = = =28.71kw
(2) Motor power PC= P = × 28.71=33kw wherein:
k-motor residue coefficient, coefficient K = 1.15;
-transmission efficiency factor, transmission efficiency = 1;
(3) torque =9550k =9550 × 1.1 × 33 ÷ 1478=234N ∙ m; wherein:
k-safety factor, K = 1.1;
(4) impeller shaft hole diameter d = =0.042 m; wherein:
allowable shear stress, when 3Cr13 is selected as the material, is not less than 15 MPa.
7. The hydraulic model of a high-efficiency chemical centrifugal pump according to claim 1, wherein the outer diameter of the impeller is 330mm, and the specific calculation process is as follows:
KD2=9.35()-1/2=8.91
D2= KD28.91 =0.33 m; wherein:
d2 — mean impeller exit diameter;
q is the flow rate of the pump, m 3/s;
n-impeller speed, rpm;
n s-Pump specific number of revolutions.
8. The hydraulic model of a high-efficiency chemical centrifugal pump according to claim 1, wherein the outlet width of the impeller is 30mm, and the specific calculation process is as follows:
Kb2=0.64（）5/6=0.693
b2= Kb Kb2=1.15 × 0.693 × =0.0295 ≈ 0.03 m; wherein:
b 2-mean width of impeller exit;
q is the flow rate of the pump, m 3/s;
n-impeller speed, rpm;
n s-Pump specific revolutions;
kb — correction factor, Kb = 1.15.
9. The hydraulic model of a high-efficiency chemical centrifugal pump according to claim 1, wherein the pump body is a spiral annular pumping chamber with a variable cross section, the base circle of the pumping chamber is 340mm, the cross section area of the maximum flow section of a volute chamber in the pump body is 4957.3mm2, the length of a diffusion section of the volute chamber is 200mm, the volute installation angle is 22, the diameter of an inlet of the pump body is 150mm, the diameter of an outlet of the pump body is 125mm, and the center of the pump body is 355mm from the center to the plane of the outlet.
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