The invention belongs to the research field of centrifugal pump, and specifically relates to an optimized design method of jet self-priming centrifugal pump. In particular, the invention relates to the optimization method of the impeller inlet, including tilt optimization setting on front cover and back cover of impeller, and Splitter blades are arranged between long blades.
As a general purpose machine, pump is mainly used to convert the mechanical energy of the original motor into the energy of liquid. It has been widely used in various sectors of the national economy and high-tech fields such as space ships. According to statistics, pumps account for 18% of the total power generation, so the energy saving potential is huge. For a jet self-priming centrifugal pump, the head when valve is closed should be considered in addition to the efficiency. The present invention improves the efficiency of the jet self-priming centrifugal pump by optimizing the impeller inlet and cover plate structure, and proposes a optimization design method of splitter blade to improve the head when valve is closed under the condition that the outer diameter of the impeller remains unchanged.
Upon retrieval, the present invention related patent applications are: “a complex variable curvature pump impeller design method of low specific speed reason, public number: CN103994099A splitter blade is used in the invention, the invention of the design is carried out for the splitter blade Angle, inclination Angle in (18°˜24°), within the scope of the blade Angle in (70°˜82°) range. The invention USES a fixed Angle range to select the parameters of sideling placed blade and scroll of blade. In addition, the invention published by zing shubing, zhu rongsheng, Yang ailing and others is named as a design method of a long-blade rotary flow pump. The public number is CN103541925A. the design of Splitter blades are made to improve the efficiency of rotary flow pump.
Comparing with the relevant patent, the invention intends to the selection of geometric parameters of the Splitter blades. The invention adopts inlet diameter of Splitter blades, length of Splitter blade, circumferential position deviation of Splitter blade, and inclination Angle parameters of Splitter blade. The invention uses the quantitative relation of geometric parameters between the Splitter blade and the long blade to determine the parameter range of the Splitter blade, so as to achieve the best effect. In addition, in order to further reduce pump Import energy loss and disc friction loss, the present invention proposes an optimization design method for pump inlet and front and rear cover plate by searching for related technologies that are not similar to the invention. The invention improves the performance of the original jet flow self-priming centrifugal pump by designing the geometric parameters above, and achieves the goal of improving the head, increasing the pump capacity and reducing the noise.
The purpose of the invention is to provide an optimal design method for the jet self-priming centrifugal pump in the light of such problems as large Import energy loss on the jet self-priming centrifugal pump, the dead point head can not raise when the impeller external diameter D2 are fixed and the noise. Cutting at the impeller inlet, setting tilt of front cover and back cover, and optimal design of Splitter blade. The invention provides the cutting length of the vertical and horizontal sides called a, b. Pitch position diameter of front and rear cover plate called D. The thickness of the front cover plate and the back cover plate wall at the exit of the tilting optimized rear impeller called δ1, The number of long blades after setting the splitter blade called Z1, The scroll of long blade after optimized called Φ1, The inlet diameter of the splitter blades called Dsi, The length of arc of split blades called S2, The circumferential offset Angle of splitter blades called θ1, The tilt Angle of splitter blades called a2, and the parameter selection and optimization method of the thickness of the splitter blades. The invention is simple to implement and can effectively improve the performance of the jet self-priming centrifugal pump.
The technical scheme of the invention: an optimized design method of let self-priming centrifugal pump including the optimization of the impeller blade.
To optimize the impeller blade is to set splitter blades between the long blades of the pump including the choice of the number of blades Z, the long blade inclusion after optimized Φ1, the inlet diameter of the splitter blades Dsi, the length of arc of split blades S2, the circumferential offset angle of splitter blades θ1 and the tilt angle of splitter blades a2.
The relationship between the number of long blades on the optimized pump Z2 and the number of long blades in the original pump Z1 is as follows:
Z
2
=Z′*Z
1 (5)
Z′ means the correction coefficient and Z′=0.6;
Optimized scroll of long blade Φ1 and the original model of scroll of long blade Φ, original pump long blade number Z1, optimized number of long blade on the pump Z2 are satisfied the following equation:
Φ1=Z1Φ/KΦZ2 (6)
KΦ means the coefficient of the scroll of blade and KΦ=0.9426;
The impeller inlet diameter of the splitter blades Dsi and the impeller outlet diameter D2 are satisfied the following equation:
D′=D
si
/D
2 (7)
D′ means the correction coefficient and D=(0.4˜0.8)
The length of arc of split blades S, and the length of arc of long blades S1 are satisfied the following equation:
K
5
=S
2
/S
1 (8)
K5 means the correction coefficient and K5=(0.4˜0.8)
The circumferential offset angle of splitter blades θ1 and the angle between two adjacent long blades θ are satisfied the following equation:
K
6=θ1/θ (9)
K6 means the correction coefficient and K6=(0.4˜0.6)
The tilt angle of splitter blades a2 and the tilt angle of long blades a1 are satisfied the following equation:
K
7
=a
2
/a
1 (10)
K7 means the correction coefficient and K7=(0.5˜0.9)
In particular, the inlet and outlet thickness of the splitter blades is consistent with that of the inlet and outlet thickness of the long blades.
And, the invention also includes cutting the impeller through the water side, further the vertical side cutting length a and the hub diameter of impeller dh are satisfied the following equation:
K
1
=a/d
h (1)
K1 means the correction coefficient and K1=(0.01˜0.05)
Moreover, the horizontal side cutting length b and the hub diameter of impeller dh are satisfied the following equation:
K
2
=b/d
h (2)
K2 means the correction coefficient and K2=(0.02˜0.08)
The impeller front shroud and the impeller back shroud were designed by tilting, It Includes the design of the pitch position diameter Dt. And the design of the pitch position diameter of the impeller front shroud and the impeller back shroud Dt and the impeller outlet diameter D2 are satisfied the following equation:
K
3
=D
t
/D
2 (3)
K3 means the correction coefficient and K3=(0.75˜0.95)
Also, the design of tilting includes the thickness of the impeller front shroud and the impeller back shroud by this way, the optimized thickness of the impeller front shroud and the impeller back shroud δ1 and the original thickness of the impeller front shroud and the impeller back shroud δ2 are satisfied the following equation:
K
4=δ1/δ2 (6)
K4 means the correction coefficient and K4=(0.6˜0.9)
That mentioned above, The calculated result of the optimized number of long blade on the pump Z2 is taken upward. It is worth noting that the number of long blades on the optimized pump Z2 is equal to the number of splitter blades Z3
Compared with the existing technology, the beneficial effect of the invention:
In the diagram, 1 means impeller inlet; 2 means impeller front shroud; 3 means impeller back shroud; 4 means splitter blades; 5 means long blade of the original model; 6 means long blade of the Optimized model.
Further details of the invention are given below in combination with attached drawings and specific implementation cases, but the scope of protection of the invention is not limited.
The invention relates to an optimized design method for a jet self-priming centrifugal pump which includes the optimization of the inlet 1, the impeller front shroud 2, the impeller hack shroud 3 and the blades.
when the liquid passes through the inlet side of the impeller, it will produce shock and then impact loss. In order to reduce the loss, the invention cuts the inlet side of the impeller to make it a buffer zone, so that the loss is much smaller when the liquid flows through this area, which can effectively reduce the impact loss of the inlet.
In order to make the inlet into the desired buffer zone, the cutting scheme adopted in the invention is that we select the appropriate cutting length on both sides (the vertical side and the horizontal side) of the inlet, the cutting length of the vertical sides called a, and the cutting length of the horizontal sides called b. And, the vertical side cutting length a and the horizontal side cutting length b is determined by the quantitative relation between a, b and the huh diameter the hub diameter of impeller dh, and they are satisfied the following equation:
K
1
=a/d
h (1)
dh is the hub diameter of impeller, mm
K1 means the correction coefficient and K1=(0.01˜0.05)
K
2
=b/d
h (2)
K2 means the correction coefficient and K2=(0.02˜0.08)
When the impeller rotates, there is friction loss between the outer surface of the front shroud and the hack shroud of the impeller and the liquid by the rapid rotating speed of the impeller. The loss is related to the diameter of the impeller, which is called disk friction loss. The invention optimizes the tilting design of the front shroud and the back shroud of the impeller so as to reduce the friction loss without changing the outside diameter of the impeller.
For setting the slant optimization parameters of the front shroud and the back shroud of the impeller, in the first, the invention determines the pitch position diameter Dt, and then determines the optimized thickness of the impeller front shroud and the impeller back shroud δ1. When these two parameters are determined, the slant design of the front shroud and the back shroud cover plate is also determined.
For selecting the pitch position diameter Dt, the invention establishes a quantitative relation with the impeller outlet diameter D2:
K
3
=D
t
/D
2 (3)
K3 means the correction coefficient and K3=(0.75˜0.95)
Therefore, in the case that the impeller outlet diameter is known as D2, the pitch position diameter Dt can be determined by the correction coefficient K3.
For the selection of the parameters of the optimized thickness of the impeller front shroud and the impeller back shroud δ1, the present invention establishes the δ1 and the original thickness of the original thickness of the impeller front shroud and the impeller back shroud δ2 to a quantitative relationship, and they are satisfied the following equation:
K
4=δ1/δ2 (4)
K4 means the correction coefficient and K4=(0.6˜0.9)
Therefore, δ1 can be determined by the correction coefficient K4 when the δ2 is known.
What optimizes the impeller blades is that the splitter blades are arranged between the long blades of the original model the invention includes the choice of the number of blades Z, the scroll of long blade after optimized Φ1, the inlet diameter of the splitter blades Dsl, the length of arc of splitter blades S2, the circumferential offset angle of splitter blades θ1, the tilt angle of splitter blades a2, and the optimized thickness of splitter blades at the inlet and outlet.
The design method of setting splitter blades between long blades is adopted to increase the head when the valve is completely closed and reduce the blockage at the inlet of the impeller. The methods adopted are as follows:
With the increase of blade number of impeller, the head increases obviously. However, too many blades will cause a large amount of hydraulic friction loss, which, on the contrary, reduces the efficiency of the pump. At the same time, the increase of the number of blades will lead to the increase of power, so it is particularly important to select an appropriate number of blades Z, In order to change the outside diameter and not overpower, a new method of adding splitter blades is proposed. A quantitative relationship was established between original pump long blade number Z1 and optimized number of long blade on the pump Z2, the relation is used to determine the optimized number of blades Z2. The expression is set up as follows:
Z
2
=Z′*Z
1 (5)
Z′ means the correction coefficient and Z′=0.6;
The calculated result of Z2 is taken upward. Since the number of the splitter blade is equal to Z2, Z3 can be determined when Z2 is known.
In order to determine the optimized scroll of long blade Φ1, optimized scroll of long blade Φ1 and the original model of scroll of long blade Φ, original pump long blade number Z1, optimized number of long blade on the pump Z2 are adopted to establish a quantitative relationship:
Φ1=Z1Φ/KΦZ2 (6)
KΦ means the coefficient of the scroll of blade and KΦ=0.9426;
So after the known Φ, Z1 and the Z2 calculated by Z′,Φ1 can be determined. The impeller inlet diameter of the splitter blades Dsi relates to the length of the splitter blades. Theoretically speaking, the longer the blade length is, the bigger the head, However, it can be seen from the study that the inlet will be blocked and the head will be reduced because of the too long splitter blades, which will also lead to a decrease in efficiency. But, if the splitter blade is too short it will not improve the structure of jet—wake at the outlet and improve the efficiency of the pump. Therefore, the quantitative relation between the impeller inlet diameter of the splitter blades Dsi and the impeller outlet diameter D2 is proposed to determine Dsi, they are satisfied the following equation:
D″=D
si
/D
2 (7)
D′ means the correction coefficient and D′=(0.4˜0.8)
So you can determine Dsi by D″ when you know D2.
When choosing the parameters of the length of arc of split blades S2, a quantitative relationship between the length of arc of splitter blades S2 and the length of arc of long blades S1 is proposed. The relationship is as follows:
K
5
=S
2
/S
1 (8)
K5 means the correction coefficient and K5=(0.4˜0.8)
So you can determine S2 by K5 when you know S1.
According to the flow slip theory in the centrifugal pump, the velocity distribution in the impeller passage is not uniform, so the splitter blade cannot be arranged in the middle of the flow passage, and it needs to be offset to the back of the long blade, which is conducive to improving the “jet-wake” structure at the outlet and improving the performance of the pump. The invention determines the circumferential position of the splitter blade by the ratio of the circumferential offset Angle of splitter blades θ1 to the angle between two adjacent long blades θ, and the relationship is as follows:
K
6=θ1/θ (9)
K6 means the correction coefficient and K4=(0.4˜0.6)
So you can determine θ1 by K6 when you know θ, and the circumferential offset position of the splitter blade can be determined.
The tilting position of the splitter blade can be determined by the tilt angle of splitter blades a2, so the quantization relationship is established by the tilt angle of splitter blades a2 and the tilt Angle of long blades a1:
K
7
=a
2
/a
1 (10)
K7 means the correction coefficient and K7=(0.5˜0.9)
The invention designs the inlet and outlet thickness of the splitter blade. For the invention, the inlet and outlet thickness of the splitter blade is consistent with the long blade.
The implementation process of the invention is illustrated by taking low specific speed Jet self-priming centriftigal pump as an example. And the specific parameters of the pump are as follows: rated power is 800 w, specific speed is 32, head H is 121.39 ft, mass flow rate Q is 3700 L/H, speed n is 2775 r/m, efficiency η is 14.3%, impeller diameter D2 is 121 mm, width of blade outlet b2 is 4 mm, the original model of scroll of long blade Φ is 100°, blade inlet angle β1 is 19.3°, blade outlet angle β2 is 35°, the hub diameter the hub diameter of impeller dh is 19 mm, number of blades Z is 6, the original thickness of the impeller front shroud and the impeller back shroud δ2 is 2 mm.
As is shown in
From
From
From
From
From
From
From
From
The inlet and outlet thickness of the splitter blade is consistent with the long blade in the invention. And the thickness of the inlet of the splitter blade is 3 mm, the thickness of the outlet of the splitter blade is 7 mm, the thickness in the middle of the splitter blade is 53 mm.
As is shown in awe 4, we can see the performance curve of the original model of jet self-priming centrifugal pump, and the
Number | Date | Country | Kind |
---|---|---|---|
201710968463.0 | Oct 2017 | CN | national |
Filing Document | Filing Date | Country | Kind |
---|---|---|---|
PCT/CN2017/108519 | 10/31/2017 | WO | 00 |