CN113202787A - Numerical simulation prediction method for necessary cavitation allowance of volute type centrifugal pump - Google Patents

Numerical simulation prediction method for necessary cavitation allowance of volute type centrifugal pump Download PDF

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CN113202787A
CN113202787A CN202110630105.5A CN202110630105A CN113202787A CN 113202787 A CN113202787 A CN 113202787A CN 202110630105 A CN202110630105 A CN 202110630105A CN 113202787 A CN113202787 A CN 113202787A
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blade
value
pressure
cavitation
inlet
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CN113202787B (en
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周佩剑
王浩
牟介刚
蒋登辉
罗会灿
沈盟淞
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China Jiliang University
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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
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0088—Testing machines
    • 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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T90/00—Enabling technologies or technologies with a potential or indirect contribution to GHG emissions mitigation

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The invention discloses a numerical simulation prediction method for the necessary cavitation allowance of a volute type centrifugal pump. The method mainly comprises the following steps: modeling, and deriving a fluid domain; performing mesh division in CFX; setting the reference pressure to be 0Pa, carrying out constant calculation on the model without adding a cavitation model; selecting a proper suction surface of the blade to perform area integration on the pressure value of the suction surface through post-processing to obtain a surface pressure equalizing value; adding a cavitation model, and setting a reference air pressure value; and recalculating, and resetting a new reference air pressure value to a point that the lift is reduced by 3% according to whether the result lift meets the condition. The invention can greatly save the calculation time and improve the calculation efficiency, and simultaneously adopts the method of changing the reference air pressure value to calculate the necessary cavitation allowance of the pump. Generally, the necessary cavitation balance value of the pump can be obtained by not more than five times of calculation.

Description

Numerical simulation prediction method for necessary cavitation allowance of volute type centrifugal pump
Technical Field
The invention relates to a novel centrifugal pump cavitation numerical calculation method, in particular to a numerical simulation prediction method for the necessary cavitation allowance of a volute type centrifugal pump.
Background
The cavitation margin is an important parameter of the pump, and refers to the surplus energy per unit weight of liquid at the pumping inlet in excess of the vaporization pressure, which reflects the cavitation performance of the pump. The smaller the pump cavitation margin, the stronger the cavitation resistance. According to the size of the cavitation allowance, the allowable height of the pump installation can be determined, and the method has important significance in practical engineering application. The pump cavitation performance directly influences whether the pump can operate as expected or not, which is related to the state of the whole system, and once cavitation calculation is inaccurate, the imaginable result can be caused. In the actual industry, a series of measures are taken to reduce the cavitation margin, and if an accurate and satisfactory value of the cavitation margin is not obtained, the performance of the pump is seriously reduced, and even the operation of the pump is interrupted. Therefore, it is important for the pump industry to be able to quickly and accurately obtain the size of the pump cavitation margin.
However, the conventional methods include a CFD simulation method and an experimental measurement method, where CFD is equivalent to a "virtual" experiment performed on a computer to simulate the actual fluid flow condition, and the experimental measurement cost is relatively high, so that the CFD simulation is usually used to obtain the cavitation margin of the pump. Now, the cavitation allowance when the head is reduced by 3% is generally taken as the necessary cavitation allowance of the pump, namely NPSHR。
The CFD is adopted to simulate the process of obtaining the necessary cavitation allowance, the existing method mostly sets the total pressure of the outlet to gradually reduce, and the simulation is carried out for a plurality of times until the total pressure value of the outlet reduces the lift by 3 percent. Because the lift is gradually reduced and then rapidly reduced along with the total pressure of the outlet in the reducing process, the lift reduction near a point of 3% can be obtained only by carrying out the process for many times, even more than ten times, in most cases, the method has low efficiency, consumes a large amount of time and resources, and ensures the precision of a specific simulation result difficultly.
Disclosure of Invention
In order to solve the problem of low efficiency in the process of obtaining the cavitation allowance according to the traditional CFD simulation method, the invention adopts a reference air pressure value and utilizes the reference air pressure value to calculate the cavitation allowance.
The invention specifically comprises the following steps:
the method comprises the following steps: establishing a fluid domain
Modeling a volute type centrifugal pump, and setting an initial position between the edge of a blade and a partition tongue;
connecting the top point of the partition tongue with the center of the blade inlet circle, connecting all the top points of the blades with the center of the blade inlet circle, ensuring that the minimum included angle between the connecting line of the top point of the partition tongue and the center of the blade inlet circle and the connecting line of the top point of the blades and the center of the blade inlet circle is between 1 and 5 degrees, and exporting the fluid domain file.
Step two: mesh partitioning
And carrying out grid division on the exported fluid domain file, carrying out grid refinement on the blade and the inlet and outlet areas, dividing out fine boundary layer grids, and carrying out quality improvement on all the grids.
Step three: constant calculation without adding cavitation model
Importing the grid file obtained in the step two into a software CFX, setting an initial reference air pressure value to be 0 under the condition of not adding a cavitation model, setting outlet static pressure according to rated lift, carrying out constant calculation to obtain a result file, and recording the lift H at the moment0And calculates the head H' that needs to be reduced to 3% while copying a result file for later use.
Step four: calculating the face pressure balance value of the selected blade
Carrying out post-processing on the result file obtained in the step three, observing the internal pressure distribution condition, and finding out the blade for integral; satisfy 1.2D on the blade for integrationin～0.75DoutThe area of the suction surface is integrated with the pressure area to obtain the surface pressure equalizing value PaWherein D isinIs the diameter of the inlet of the blade, DoutIs the vane exit diameter.
Step five: determining reference air pressure value, adding cavitation model, and calculating verification result at constant time
The surface pressure equalizing value P obtained in the fourth stepaSubtracting the saturated vapor pressure PvAs a reference pressure value Pf. In the software CFX, a reference air pressure value is set, and the constant calculation is carried out to judge whether the lift value H in the simulation result reaches the point that the lift is reduced by 3%.
Step six: and (5) performing iterative calculation, and re-selecting the reference air pressure value according to the height H of the head in the result file to judge the result.
The invention has the beneficial effects that: according to the method, the next calculation is directly carried out according to the internal cavitation pressure value instead of blindly reducing the outlet pressure according to the reason of cavitation generation, so that the calculation time can be greatly saved, the calculation efficiency is improved, and meanwhile, the method for changing the reference pressure value is adopted to calculate the necessary cavitation allowance of the pump. Generally, the necessary cavitation balance value of the pump can be obtained by not more than five times of calculation.
Drawings
FIG. 1: the flow chart of the invention;
FIG. 2: selecting an angle by the blade;
FIG. 3: the extent of pressure zone a;
FIG. 4: an integration area;
FIG. 5: the NPSH-H curve obtained by the method of gradually reducing the total outlet pressure is compared with the NPSH-H curve obtained by the method.
Detailed Description
As shown in fig. 1, in order to achieve fast and accurate acquisition of the value of the cavitation margin, the present invention provides the following steps:
the method comprises the following steps: fluid domain establishment
Modeling is carried out on the volute type centrifugal pump, an initial position between the edge of the blade and the partition tongue is set, the top point of the partition tongue and the center of the inlet circle of the blade are connected, the top points of all the blades and the center of the inlet circle of the blade are connected, the minimum value of the included angle between the connecting line of the top point of the partition tongue and the center of the inlet circle of the blade and the connecting line of the top point of the blade and the center of the inlet circle of the blade is ensured to be between 1 and 5 degrees, and a fluid domain file is led out.
Step two: mesh partitioning
And carrying out grid division on the exported fluid domain file, carrying out grid refinement on the blade and the inlet and outlet areas, dividing out fine boundary layer grids, and carrying out quality improvement on all the grids.
Step three: constant calculation without adding cavitation model
And (4) importing the grid file obtained in the step two into a software CFX, setting an initial reference air pressure value as 0 under the condition of not adding a cavitation model, setting outlet static pressure according to rated lift, performing constant calculation to obtain a result file, recording the lift value at the moment, calculating the lift required to be reduced to 3%, and copying the result file for later use.
With a given flow value Q, the nominal head HNSetting is performed in software CFX:
static pressure P at outletmThe method comprises the following steps:
Pm＝(λHN+ε)ρg,λ∈(1.0～1.1),ε∈(10～20)
wherein rho is the density of the liquid, g is the acceleration of gravity, lambda is the lift coefficient, and epsilon is the reference amount of the lift
The mass flow rate at the inlet was set to: q
The inlet total pressure can be obtained through simulation treatment: pinAnd outlet total pressure: pout
According to the relationship between the pump head and the inlet-outlet pressure, the following conditions can be obtained: head H0＝(Pout-Pin)/ρg，H0The lift obtained without adding cavitation model. Lift H' at 3% drop: h' is 0.97H0
Step four: post-treatment
Post-processing the result file obtained in the third step, observing the internal pressure distribution condition, finding out the blade for integration, and satisfying 1.2D on the bladein～0.75DoutThe suction surface area is integrated with the pressure area to obtain the surface pressure equalizing value PaWhere D isinIs the diameter of the inlet of the blade, DoutIs the vane exit diameter.
The pressure distribution on the blade can be seen through a CFD post-processing blade pressure cloud chartConnecting the center O of the impeller inlet circle with the top point of the partition tongue to obtain a straight line l, and taking the center O of the impeller inlet circle as a rotation point to respectively rotate the straight line l by 1 degree and 5 degrees clockwise and anticlockwise respectively, and recording the straight line of 1 degree clockwise as l1And the straight line rotated clockwise by 5 degrees is denoted as l2And a line rotated counterclockwise by 1 DEG is denoted by l'1Line rotated counterclockwise by 5 DEG is denoted by l'2。
Is selected to be located at1And l2Or l'1And l'2The connecting line between the tail end of the blade and the center O of the inlet circle of the impeller is marked as l3When there are a plurality of straight lines l3When it is, then use l3L is optimal when the included angle between l and l is 3 degrees3。
The suction surface of the selected blade meets 1.2Din～0.75DoutThe inner zone, i.e. the defined pressure zone range, is:
A＝∫sdt，t∈(1.2Din，0.75Dout)
t is 1.2D satisfied at the suction surface of the bladein～0.75DoutThe length of the inner area, s is 1.2D satisfied at the suction surface of the bladein～0.75DoutThe width of the inner zone; the maximum pressure value in the pressure region A is denoted as Pmax(ii) a Integrating the area of the area A to obtain the surface voltage-sharing value Pa：
Figure BDA0003103086260000031
Where A is the area of the region, AiIs an area element, phi is a zone pressure value, phiiIs the pressure element, and n is the division frequency.
Step five: determining reference air pressure value, adding cavitation model, and calculating verification result at constant time
The surface pressure equalizing value P obtained in the fourth stepaSubtracting the saturated vapor pressure PvAs a reference pressure value Pf. In the software CFX, a reference air pressure value is set, and the constant calculation is carried out to judge whether the lift value H in the simulation result reaches the point that the lift is reduced by 3%.
Setting the reference air pressure value as follows: pf＝Pa-Pv。
Step six: iterative calculation, re-selecting reference pressure value according to the height H of the head in the result file, and judging the result
1) When in use
Figure BDA0003103086260000041
When the current is over;
if H>0.97H0Taking the initial decrease Δ P00, decrease Δ P per iterationiAnd judging according to the finally obtained H, wherein i is the iteration number and is taken as:
Figure BDA0003103086260000042
considering the mechanism that the reduction amount of each iteration is too large to affect the subsequent calculation, after n iterations, the (n +1) th iteration is reduced by the amount deltaPn+1When the value is larger than a certain value, the value is halved to be used as the (n +1) th iteration reduction quantity delta Pn+1I.e. when
Figure BDA0003103086260000043
When it is taken
Figure BDA0003103086260000044
If H<0.97H0Taking the spare result file copied in the third step, and re-picking the result file based on the spare result file
Figure BDA0003103086260000045
I.e. setting a new reference air pressure value:
Figure BDA0003103086260000046
2) when in use
Figure BDA0003103086260000047
Then, the total inlet pressure P is obtained from the post-treatmentin*According to
Figure BDA0003103086260000048
From this, the necessary cavitation margin can be determined, where Pin*Is the total inlet pressure, vsFor pump inlet speed, NPSHrThe necessary cavitation margin.
The following description is given with reference to the accompanying drawings and specific examples:
taking a volute type centrifugal pump hydraulic model as an example, after modeling is completed by using three-dimensional modeling software, a CFD simulation technology is adopted to perform constant calculation of a non-cavitation model, a backup result file is calculated, a straight line connecting the circle center O of an impeller inlet circle and the top point of a baffle tongue is l, and blades positioned at +/-1-5 degrees on two sides of l are selected in post-processing, as shown in figure 2. With O as the center and the diameter of 0.75Dout、1.2DinTwo circles are drawn as boundary lines dividing the integration regions, as shown in fig. 3. For the blade meeting the conditions, the diameter of the center of circle at the edge of the blade is 0.75DoutAnd 1.2DinThe area integral of the suction surface is taken as the intersecting closed region, and the surface pressure equalizing value is obtained as shown in fig. 4. And (3) subtracting the saturated vapor pressure from the surface pressure value to serve as a reference air pressure value, adding a cavitation model for recalculation, judging whether the finally obtained lift value meets the condition, properly changing the reference air pressure value for recalculating the condition that the condition is not met, calculating all subsequent calculations on the basis of the previous step, and recalculating the first step on the basis of a backup result file for the condition that the lift is reduced too much.
Based on the graphs obtained by the traditional method and the method, as shown in fig. 5, the traditional method for reducing the outlet pressure calculates 10 times, the method calculates 5 times, but the results are similar, which shows that the method can be used as a numerical simulation prediction method for the necessary cavitation allowance of the volute type centrifugal pump.

Claims (4)

1. A numerical simulation prediction method for the necessary cavitation allowance of a volute type centrifugal pump is characterized by comprising the following steps:
the method comprises the following steps: establishing a fluid domain
Modeling a volute type centrifugal pump, and setting an initial position between the edge of a blade and a partition tongue;
connecting the top point of the partition tongue with the center of the blade inlet circle, connecting all the top points of the blades with the center of the blade inlet circle, ensuring that the minimum included angle between the connecting line of the top point of the partition tongue and the center of the blade inlet circle and the connecting line of the top point of the blades and the center of the blade inlet circle is between 1 and 5 degrees, and exporting a fluid domain file;
step two: mesh partitioning
Carrying out grid division on the exported fluid domain file, carrying out grid refinement on the blade, the inlet and outlet areas, dividing out fine boundary layer grids, and carrying out quality improvement on all the grids;
step three: constant calculation without adding cavitation model
Importing the grid file obtained in the step two into a software CFX, setting an initial reference air pressure value to be 0 under the condition of not adding a cavitation model, setting outlet static pressure according to rated lift, carrying out constant calculation to obtain a result file, and recording the lift H at the moment0Calculating the lift H' required to be reduced to 3%, and copying a result file for later use;
step four: calculating the face pressure balance value of the selected blade
Carrying out post-processing on the result file obtained in the step three, observing the internal pressure distribution condition, and finding out the blade for integral; satisfy 1.2D on the blade for integrationin～0.75DoutThe area of the suction surface is integrated with the pressure area to obtain the surface pressure equalizing value PaWherein D isinIs the diameter of the inlet of the blade, DoutIs the blade exit diameter;
step five: determining reference air pressure value, adding cavitation model, and calculating verification result at constant time
The surface pressure equalizing value P obtained in the fourth stepaSubtracting the saturated vapor pressure PvAs a reference pressure value Pf(ii) a Setting a reference air pressure value in a software CFX, and calculating regularly to judge whether the lift value H in the simulation result reaches a point that the lift is reduced by 3%;
step six: and (3) iterative calculation, namely, according to the height H of the head in the result file, reselecting a reference air pressure value, and judging the result, specifically:
1) when in use
Figure FDA0003103086250000011
When the temperature of the water is higher than the set temperature,
if H>0.97H0Taking the initial decrease Δ P00, decrease Δ P per iterationiAnd judging according to the finally obtained H, wherein i is the iteration number and is taken as:
Figure FDA0003103086250000012
if H<0.97H0Taking the spare result file copied in the third step, and re-picking the result file based on the spare result file
Figure FDA0003103086250000013
I.e. setting a new reference air pressure value:
Figure FDA0003103086250000021
2) when in use
Figure FDA0003103086250000022
Then, the total inlet pressure P is obtained from the post-treatmentin*According to
Figure FDA0003103086250000023
From this, the necessary cavitation margin can be determined, where Pin*Is the total inlet pressure, vsFor pump inlet speed, NPSHrρ is the liquid density and g is the acceleration of gravity, which is the necessary cavitation margin.
2. The method for predicting the required cavitation margin of the volute centrifugal pump according to the claim 1, characterized in that: the third step is specifically as follows:
with a given flow value Q, the nominal head HNSetting outlet static pressure and inlet mass flow in a software CFX;
and calculating the lift value without adding the cavitation model according to the relation between the pump lift and the inlet and outlet pressure.
3. The method for predicting the required cavitation margin of the volute centrifugal pump according to the claim 1, characterized in that: the fourth step is specifically:
after CFD, processing the blade pressure cloud picture to obtain the pressure distribution on the blade;
setting the circle center O of the impeller inlet circle and the peak of the partition tongue as a straight line l, and rotating the straight line l by 1 degree and 5 degrees clockwise and anticlockwise respectively by taking the circle center O of the impeller inlet circle as a rotating point; wherein the straight line rotated clockwise by 1 degree is denoted as l1And the straight line rotated clockwise by 5 degrees is denoted as l2And a line rotated counterclockwise by 1 DEG is denoted by l'1Line rotated counterclockwise by 5 DEG is denoted by l'2Choose to be located at l1And l2Or l'1And l'2The blade in between, the blade is the blade for integration;
meets 1.2D at the suction surface of the bladein～0.75DoutThe inner zone, i.e. the defined pressure zone range, is:
A＝∫sdt，t∈(1.2Din，0.75Dout)
t is 1.2D satisfied at the suction surface of the bladein～0.75DoutThe length of the inner area, s is 1.2D satisfied at the suction surface of the bladein～0.75DoutThe width of the inner zone;
integrating the area of the area A to obtain the surface voltage-sharing value Pa：
Figure FDA0003103086250000024
Where A is the area of the region, AiIs an area element, phi is a zone pressure value, phiiIs the pressure element, and n is the division frequency.
4. The method for predicting the required cavitation margin of the volute centrifugal pump according to the claim 3, characterized in that: in step six, considering that the reduction quantity of each iteration is too large to influence the mechanism of subsequent calculation, after the iteration is performed for n times, the reduction quantity delta P of the (n +1) th iteration isn+1When the value is larger than a certain value, the value is halved to be used as the (n +1) th iteration reduction quantity delta Pn+1I.e. when
Figure FDA0003103086250000031
When it is taken
Figure FDA0003103086250000032
PmaxThe maximum pressure value over the suction surface area.
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