CN117436210A - Combined design method and device for widening flow grooves and impellers - Google Patents
Combined design method and device for widening flow grooves and impellers Download PDFInfo
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Abstract
The invention provides a combined design method and device for a widened flow groove and an impeller, which are used for determining a blade load DP0b from a blade top inlet position O point to a slotting position A point of the widened flow groove and two key control factors of surge flow, wherein the slotting position A point of the widened flow groove is determined according to a surge mechanism. In the process of carrying out joint simulation on the geometric model of the impeller and the geometric model of the widened flow groove, if the performance curve of the impeller obtained by simulation does not meet the preset performance requirement, adjusting the position of the point A and/or DP0b, modifying the corresponding geometric model according to the adjusted parameters, and then carrying out simulation until the performance curve obtained by simulation meets the preset performance requirement, completing joint design on the widened flow groove and the impeller, reducing design time, ensuring impeller efficiency and simultaneously obviously improving the effect of widened flow.
Description
Technical Field
The invention relates to the technical field of engines, in particular to a combined design method and device for widening a flow groove and an impeller.
Background
High power density high speed engines are increasingly being used. After the rotation speed range of the engine is increased, the Map width of the gas compressor is required to be large enough, and the flow groove is widened, so that the flow is effectively widened.
The extent to which the flow grooves widen the flow is extremely related to the design of the impeller in addition to the structure of the flow grooves themselves. One conventional design approach is to continually iteratively approximate the final design objective by adjusting the geometry of the widening flow slot and impeller, with a long design cycle and relying on designer experience. In another design method, after the impeller is designed, the flow groove structure is increased and widened at a certain position, and the structure is finely adjusted to widen the flow, so that the design method obviously cannot achieve the optimal effect of the system. Therefore, there is a need for an efficient method of optimizing and widening the flow channels and impeller structures to achieve system optimization.
Disclosure of Invention
In view of the above, the present invention provides a combined design method and device for widening flow grooves and impellers, which can reduce design time, ensure impeller efficiency and simultaneously remarkably improve flow widening effect.
In order to achieve the above purpose, the specific technical scheme provided by the invention is as follows:
in a first aspect, an embodiment of the present invention provides a method for designing a combination of a flow channel and an impeller, including:
determining the size of a meridian runner of the impeller according to the initial geometric parameters of the impeller;
Setting blade parameters of an impeller;
determining a blade shape according to the blade parameters;
determining a geometric model of the impeller according to the size of the radial flow channel of the impeller, the blade parameters and the blade shape;
simulating a geometric model of the impeller to obtain a first performance curve of the impeller;
if the first performance curve does not meet the first preset performance requirement, adjusting the blade parameters, and returning to execute the step of determining the blade shape according to the blade parameters;
if the first performance curve meets a first preset performance requirement, determining the geometric parameters of the widened flow grooves, and obtaining a geometric model of the widened flow grooves, wherein the geometric parameters of the widened flow grooves at least comprise the positions of the A points of the slotting positions;
performing joint simulation on the geometric model of the impeller and the geometric model of the widened flow groove to obtain a second performance curve of the impeller;
and if the second performance curve does not meet the second preset performance requirement, adjusting the position of the point A and/or the blade load DP0b from the position O of the blade top inlet to the position A of the slotting position of the widened flow channel, modifying the corresponding geometric model according to the adjusted parameters, and then simulating until the second performance curve meets the second preset performance requirement, thereby completing the joint design of the widened flow channel and the impeller.
In some embodiments, the determining the blade shape from the blade parameters includes:
according to the load distribution of the blades at the blade top, 50% of blade height and blade root along the streamline direction in the blade parameters, the theoretical annular difference value of the inlet and outlet of the blades, the number of the blades, the radial flow channel size of the impeller, the design point flow, the design rotating speed, the inclination angle of the impeller at the tail edge and the enthalpy difference load of the blades at all positions along the streamline direction are calculated;
determining the surface speed distribution of the blade according to enthalpy difference loads at various positions of the blade along the streamline direction;
the blade shape is determined from the blade surface velocity profile.
In some embodiments, the adjusting the blade parameter includes:
if the first performance curve represents that the surge flow is smaller than the target surge flow in the first preset performance requirement, increasing the load of a key position in the load distribution of the blade along the streamline direction in the blade parameter;
if the first performance curve represents that the surge flow is larger than the target surge flow in the first preset performance requirement, reducing the load of the key position;
and if the first performance curve represents that the blocking allowance is smaller than the target blocking allowance in the first preset performance requirement, increasing the flow of the design point in the blade parameter.
In some embodiments, the adjusting the position of the point a and/or the blade load DP0b from the position O of the blade tip inlet to the position a of the slot of the widened flow slot, and modifying the corresponding geometric model according to the adjusted parameters, and then performing simulation includes:
if the surge flow represented by the second performance curve is smaller than the target surge flow in the second preset performance requirement, adjusting the position of the point A to reduce the axial distance between the point O and the point A, obtaining an adjusted geometric model of the widened flow groove, and returning to execute the step of carrying out joint simulation on the geometric model of the impeller and the geometric model of the widened flow groove;
if the axial distance between the O point and the A point reaches the minimum value, the second performance curve still does not meet the second preset performance requirement, the DP0b is reduced, and the step of determining the shape of the blade according to the blade parameter is performed again until the second performance curve meets the second preset performance requirement, so that the joint design of the widened flow groove and the impeller is completed.
In some embodiments, the adjusting the position of the point a and/or the blade load DP0b from the position O of the blade tip inlet to the position a of the slot of the widened flow slot, and modifying the corresponding geometric model according to the adjusted parameters, and then performing simulation further includes:
If the surge flow represented by the second performance curve is larger than the target surge flow in the second preset performance requirement, adjusting the position of the point A to increase the axial distance between the point O and the point A, obtaining an adjusted geometric model of the widened flow groove, and returning to execute the step of carrying out joint simulation on the geometric model of the impeller and the geometric model of the widened flow groove;
if the axial distance between the O point and the A point reaches the maximum value, the second performance curve still does not meet the second preset performance requirement, the DP0b is increased, and the step of determining the shape of the blade according to the blade parameter is performed again until the second performance curve meets the second preset performance requirement, so that the combined design of the widened flow groove and the impeller is completed.
In a second aspect, an embodiment of the present invention provides a combined design apparatus for widening a flow channel and an impeller, including:
the meridian flow passage determining unit is used for determining the size of the meridian flow passage of the impeller according to the initial geometric parameters of the impeller;
a blade parameter setting unit for setting blade parameters of the impeller;
a blade shape determining unit for determining a blade shape according to the blade parameter;
The impeller model determining unit is used for determining a geometric model of the impeller according to the size of the radial flow channel of the impeller, the blade parameters and the blade shape;
the first simulation unit is used for simulating the geometric model of the impeller to obtain a first performance curve of the impeller;
the first parameter adjusting unit is used for adjusting the blade parameters and triggering the blade shape determining unit if the first performance curve does not meet a first preset performance requirement;
the flow groove model determining unit is used for determining the geometric parameters of the widened flow groove if the first performance curve meets a first preset performance requirement to obtain a geometric model of the widened flow groove, wherein the geometric parameters of the widened flow groove at least comprise the position of a slotting position A;
the second simulation unit is used for carrying out joint simulation on the geometric model of the impeller and the geometric model of the widened flow groove to obtain a second performance curve of the impeller;
and the second parameter adjusting unit is used for adjusting the blade load DP0b from the position of the point A and/or the position O of the blade top inlet to the position A of the slotting of the widened flow groove if the second performance curve does not meet the second preset performance requirement, and triggering the blade shape determining unit or the second simulation unit after modifying the corresponding geometric model according to the adjusted parameters until the second performance curve meets the second preset performance requirement, so as to complete the joint design of the widened flow groove and the impeller.
In some embodiments, the blade shape determining unit is specifically configured to calculate enthalpy difference loads at various positions of the blade along the streamline direction according to load distribution of the blade along the streamline direction at the blade tip, 50% of blade height and blade root in the blade parameters, theoretical annular difference values of blade inlets and outlets, number of blades, radial runner size of the impeller, design point flow, design rotation speed, impeller inclination angle at the trailing edge; determining the surface speed distribution of the blade according to enthalpy difference loads at various positions of the blade along the streamline direction; the blade shape is determined from the blade surface velocity profile.
In some embodiments, the first parameter adjustment unit is specifically configured to increase a load at a critical position in a load distribution of the blade in the blade parameter along the streamline direction if the first performance curve indicates that the surge flow is less than a target surge flow in a first preset performance requirement, and decrease the load at the critical position if the first performance curve indicates that the surge flow is greater than the target surge flow in the first preset performance requirement; and if the first performance curve represents that the blocking allowance is smaller than the target blocking allowance in the first preset performance requirement, increasing the flow of the design point in the blade parameter.
In some embodiments, the second parameter adjustment unit is specifically configured to:
if the surge flow represented by the second performance curve is smaller than the target surge flow in the second preset performance requirement, adjusting the position of the point A so as to reduce the axial distance between the point O and the point A, obtaining an adjusted geometric model of the widened flow groove, and triggering the second simulation unit;
if the axial distance between the O point and the A point reaches the minimum value, the second performance curve still does not meet the second preset performance requirement, the DP0b is reduced, the blade shape determining unit is triggered until the second performance curve meets the second preset performance requirement, and the combined design of the widened flow groove and the impeller is completed.
In some embodiments, the second parameter adjustment unit is further specifically configured to:
if the surge flow represented by the second performance curve is larger than the target surge flow in the second preset performance requirement, adjusting the position of the point A so as to increase the axial distance between the point O and the point A, obtaining an adjusted geometric model of the widened flow groove, and triggering the second simulation unit;
if the axial distance between the O point and the A point reaches the maximum value, the second performance curve still does not meet the second preset performance requirement, the DP0b is increased, the blade shape determining unit is triggered until the second performance curve meets the second preset performance requirement, and the combined design of the widened flow groove and the impeller is completed.
Compared with the prior art, the invention has the following beneficial effects:
the invention discloses a combined design method and a device for a widened flow groove and an impeller, which are used for determining a blade load DP0b from a blade top inlet position O point to a slotting position A point of the widened flow groove and determining two key control factors of surge flow at the slotting position A point of the widened flow groove according to a surge mechanism. After the blade parameters are set, determining a geometric model of the impeller, simulating the geometric model of the impeller, if a first performance curve of the impeller obtained through simulation does not meet a first preset performance requirement, adjusting the blade parameters until the first performance curve of the impeller obtained through simulation meets the first preset performance requirement, determining geometric parameters of a widened flow groove comprising the position of a point A, obtaining the geometric model of the widened flow groove, then carrying out joint simulation on the geometric model of the impeller and the geometric model of the widened flow groove, if a second performance curve of the impeller obtained through simulation does not meet a second preset performance requirement, adjusting the position of the point A and/or DP0b, modifying the corresponding geometric model according to the adjusted parameters, and then carrying out simulation until the second performance curve meets the second preset performance requirement, completing joint design of the widened flow groove and the impeller, and obviously improving the effect of the widened flow while reducing design time and guaranteeing the efficiency of the impeller.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are required to be used in the embodiments or the description of the prior art will be briefly described below, and it is obvious that the drawings in the following description are only embodiments of the present invention, and that other drawings can be obtained according to the provided drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic view of a fluid analysis of a region near surge line provided by the present invention;
FIG. 2 is a schematic view of the top segment of the impeller and the shape of the meridional flow path according to the present invention;
FIG. 3 is a schematic flow chart of a method for designing a combination of a widening flow channel and an impeller according to an embodiment of the present invention;
FIG. 4 is a schematic view of the load distribution from inlet to outlet at the tip of a blade as disclosed in an embodiment of the present invention;
FIG. 5 is a schematic view of surge line of a non-widening flow channel according to an embodiment of the present invention;
FIG. 6 is a schematic view of surge line with widened flow slots according to an embodiment of the present invention;
FIG. 7 is a schematic diagram of a non-dimensionalized tip load distribution curve disclosed in an embodiment of the present invention;
fig. 8 is a schematic structural diagram of a combined design device for widening a flow channel and an impeller according to an embodiment of the present invention.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
In order to more clearly clarify the technical solution of the present application, related concepts related to the present application are explained below.
Widening the flow grooves: the device is a device for effectively improving the operation stability of the air compressor at the air compressor end, thereby ensuring that the air compressor has a wide operation range.
The inventor has found through research that: in the area close to the surge line, the fluid flow direction is shown in fig. 1, and the high-pressure backflow gas flows into the compressor inlet from the impeller through the widening flow groove, is mixed with the main flow gas and flows into the compressor to form a circulating passage, so that the stable operation of the compressor near surge is ensured, and the operation range of the compressor is widened.
Wherein P01 represents the pressure of the point A of the slotting position of the widened flow groove, and P02 represents the pressure of the point O of the inlet position of the impeller blade top.
The flow loss in the broadening flow tank is represented by DP0P, the mixing loss of main flow gas and reflux gas of the broadening flow tank is represented by DP0mix, the blade load from the point O to the point A of the blade near the shroud line (blade top line segment) is represented by DP0b, and the following mathematical relations exist among P01, P02, DP0P, DP0b and DP0 mix:
P01- DP0p-DP0mix= P02；
P01= P02+ DP0b；
DP0b= DP0p+ DP0mix。
it can be seen that DP0b is the most important design variable for controlling the surge flow, and the larger DP0b, the stronger the surge flow widening capability under the same widened flow groove structure.
The shroud line (tip line segment) position is shown in fig. 2, and if the degree of surge widening flow slot is to be changed, the pressure rise from O point to a point, that is, the blade load DP0b from O point to a point, can be increased, and the position of a point in the widening flow slot can be adjusted.
The combined design method for widening the flow groove and the impeller disclosed by the embodiment is applied to electronic equipment such as a desktop computer, a notebook computer, a tablet computer, a smart phone and the like, referring to fig. 3, and specifically comprises the following steps:
s101: determining the size of a meridian runner of the impeller according to the initial geometric parameters of the impeller;
the initial geometry of the impeller is determined based on layout space data allowed by the supercharger on the engine and historical supercharger product analysis.
The initial geometric parameters of the impeller include: impeller outlet diameter, impeller inlet diameter, impeller outlet width, blade root height at impeller inlet, impeller axial length, etc.
According to the initial geometric parameters of the impeller, the size of an impeller meridian flow passage is determined, the impeller meridian flow passage is the projection of an airflow passage of the impeller on a meridian plane, and specifically as shown in fig. 2, the left side is an impeller inlet, and the right side is an impeller outlet.
S102: setting blade parameters of an impeller;
the blade parameters of the impeller comprise the load distribution of the blades along the streamline direction, the theoretical annular difference value of the inlet and the outlet of the blades, the flow of a design point, the impeller inclination angle at the tail edge, the inlet condition (pressure and temperature), the number of the blades, the design rotating speed, the thickness distribution of the blades and the like.
Wherein:
the flow rate of the design point is the air inlet flow rate of the working point most commonly used in the running process of the engine.
The blade thickness distribution is determined according to the strength requirements of the impeller.
The load distribution of the blade along the streamline mainly comprises 3 key positions: blade root, 50% blade height, blade tip. Wherein the blade tip is the tip.
As shown in fig. 4, the load distribution from the inlet to the outlet at the top of the blade is shown, the X-axis 0-1 can be equivalent to the dimensionless distance from the inlet to the outlet of the blade of the impeller of a shroud line (blade top line segment), the integral area of the curve and the X-axis is the annular difference value of the inlet and the outlet of the blade, wherein the point a is the slotting position of the widened flow slot, and the blade load DP0b from the point O of the inlet of the top of the blade to the point a of the slotting position of the widened flow slot can be increased by increasing the integral area of the shadow part.
The annular quantity difference rvt of the blade inlet and the blade outlet is determined according to the flow pressure ratio rotating speed efficiency target of the key operating point of the engine. Specifically, the theoretical annular difference rvt = (isentropic compression power of gas per unit mass)/isentropic efficiency/(square of linear velocity of impeller) of the vane inlet and outlet is obtained from the inlet temperature pressure flow rate at the design point.
Impeller linear speed = design rotational speed x impeller outlet diameter.
S103: determining a blade shape according to the blade parameters;
the blade parameters do not include geometric parameters of the blade shape, and the geometric parameters need to be obtained according to load distribution of the blade along the streamline direction, theoretical annular quantity difference of the inlet and the outlet of the blade, and the like, and the geometric parameters are described in detail through specific embodiments.
S104: determining a geometric model of the impeller according to the size, the blade parameters and the blade shape of the meridian flow passage of the impeller;
after the blade shape is determined, a plurality of blades in the impeller can be correspondingly obtained according to the number of the blades in the blade parameters.
The size, the blade parameters and the blade shape of the radial flow channel of the impeller are input into any existing three-dimensional model design software to generate a geometric model of the impeller.
S105: simulating a geometric model of the impeller to obtain a first performance curve of the impeller;
specifically, CFD (Computational Fluid Dynamics ) simulation is performed on the geometric model of the impeller to obtain a first performance curve of the impeller.
S106: judging whether a first performance curve of the impeller meets a first preset performance requirement or not;
if the first performance curve does not meet the first preset performance requirement, execution S107: adjusting the blade parameters, and returning to execute S103;
the first preset performance requirement is that the geometric model of the impeller is only simulated without widening the flow groove, and the simulation result is required to meet the performance requirement.
Referring to fig. 5, the non-broadened flow slot surge line is determined according to engine operating points 1-N, the minimum flow of the non-broadened flow slot surge line is 0.98 x the operating point flow, the maximum flow is the operating point flow, and the target surge flow of the non-broadened flow slot surge line needs to meet the above requirements.
And judging whether the first performance curve meets a first preset performance requirement or not, and comparing surge flow of the surge line with blocking allowance.
If the first performance curve represents that the surge flow is smaller than the target surge flow in the first preset performance requirement, namely smaller than the minimum flow of the surge line of the non-broadening flow tank, the load of the critical position in the load distribution of the blade along the streamline direction in the blade parameter is increased, and if the first performance curve represents that the surge flow is larger than the target surge flow in the first preset performance requirement, namely larger than the maximum flow of the surge line of the non-broadening flow tank, the load of the critical position is reduced;
If the first performance curve represents that the blocking allowance is smaller than the target blocking allowance in the first preset performance requirement, the flow of the design point in the blade parameter is increased, and if the first performance curve represents that the blocking allowance is larger than the target blocking allowance in the first preset performance requirement, the flow of the design point in the blade parameter is reduced. The target occlusion margin may be 3%.
The key positions in the load distribution of the blade along the streamline direction comprise a blade top, a 50% blade height and a blade root.
If the first performance curve meets the first preset performance requirement, execution S108: determining geometric parameters of the widened flow grooves, and obtaining a geometric model of the widened flow grooves, wherein the geometric parameters of the widened flow grooves at least comprise positions of a slotting position A;
widening geometrical parameters of the flow channel comprises: the position of the point A, the width of the flow groove, the included angle alpha between the flow groove and the horizontal direction and the like.
As shown in fig. 2, the point O of the inlet position of the blade tip is fixed, and after the geometric model of the impeller is determined, the point X of the spatial position of the roar of the large blade is also fixed, the point a is the slotting position of the widened flow slot, and the point a is located axially behind the point X, i.e. axially to the right of the roar of the large blade.
The axis distance between the X point and the A point is represented by L-a, and the value range of the L-a is as follows: [ 0.03X axial length of impeller, 0.05X axial length of impeller ], the initial design generally sets the value of L-a as the intermediate value, and after the value of L-a is set, the position of the point A is set because the position of the point X is fixed.
The value range of the width W_p of the widened flow groove is related to the L-a, and the value range of the W_p is as follows: [0.1 XL-a, 0.2 XL-a ], the initial design is also generally set to an intermediate value.
The value range of alpha is as follows: [45 °,60 ° ], the initial design is also typically chosen to be intermediate.
The inventor finds that the sensitivity of L-a is the largest in the geometric parameters of the widened flow groove, and the sensitivity of the other two parameters W_p and alpha is smaller.
After the three important geometric parameters of the widened flow grooves are set, the geometric parameters of the widened flow grooves such as the position of the point A, W_p, alpha and the like are input into any existing three-dimensional model design software to generate a geometric model of the widened flow grooves.
S109: performing joint simulation on the geometric model of the impeller and the geometric model of the widened flow groove to obtain a second performance curve of the impeller;
and carrying out CFD joint simulation on the geometric model of the impeller and the geometric model of the widened flow groove to obtain a second performance curve of the impeller.
S110: if the second performance curve does not meet the second preset performance requirement, adjusting the position of the point A and/or the blade load DP0b from the position O of the blade top inlet to the position A of the slotting position of the widened flow channel, modifying the corresponding geometric model according to the adjusted parameters, and then simulating until the second performance curve meets the second preset performance requirement, thereby completing the joint design of the widened flow channel and the impeller.
The second preset performance requirement is the performance requirement which is required to be met by the simulation result by carrying out joint simulation on the geometric model of the impeller and the geometric model of the widened flow groove.
As shown in fig. 6, the surge line in the figure is a surge line with a widened flow groove, the engine operating points 1 and 2 … … N are located in the left area of the Map, the operating points are points with the greatest surge risk, the surge line position is calculated according to the operating points, the surge margin requirement is at least greater than 10%, and the X and Y coordinates of 3 points are assumed to be X3 and Y3 respectively.
Taking the 3 'point as an example, 3' is the corresponding point on the surge line.
The X calculation method of the 3' point is as follows:
(X3- X3’)/X3>=10%。
since X3 is known, the maximum value of X3', i.e. the upper limit of the surge line, can be found, Y3 being identical to Y3', i.e. the 3 point being identical to the 3' point on the ordinate and the abscissa being different.
And by analogy, corresponding surge points 1' to N ' can be solved according to the points 1 to N, so that a surge line is obtained, namely the surge line with a widened flow groove, a curve above the point N ' is obtained through smooth connection, and the points N+1 to Nmax are not evaluated because of no surge risk.
In theory, the control of the surge flow can be realized by adjusting the position of the point A and/or the DP0b, namely, the position of the point A and the DP0b can be controlled independently or in combination. The value range of L-a is as follows: the axial length of the impeller is 0.03 times and the axial length of the impeller is 0.05 times, that is, the adjustable range of the position of the point A is smaller, so that the position of the point A can be preferentially adjusted, and if the position of the point A cannot meet the second preset performance requirement, the DP0b is adjusted.
Therefore, according to the combined design method of the widening flow slot and the impeller disclosed by the embodiment, the blade load DP0b from the position O of the blade top inlet to the position A of the opening of the widening flow slot and the position A of the opening of the widening flow slot are determined according to the surge mechanism, and are two key control factors of the surge flow. After the blade parameters are set, determining a geometric model of the impeller, simulating the geometric model of the impeller, if a first performance curve of the impeller obtained through simulation does not meet a first preset performance requirement, adjusting the blade parameters until the first performance curve of the impeller obtained through simulation meets the first preset performance requirement, determining geometric parameters of a widened flow groove comprising the position of a point A, obtaining the geometric model of the widened flow groove, then carrying out joint simulation on the geometric model of the impeller and the geometric model of the widened flow groove, if a second performance curve of the impeller obtained through simulation does not meet a second preset performance requirement, adjusting the position of the point A and/or DP0b, modifying the corresponding geometric model according to the adjusted parameters, and then carrying out simulation until the second performance curve meets the second preset performance requirement, completing joint design of the widened flow groove and the impeller, and obviously improving the effect of the widened flow while reducing design time and guaranteeing the efficiency of the impeller.
Wherein, in the above embodiment S103: an alternative implementation of determining the blade shape from the blade parameters comprises the steps of:
a1: according to the load distribution of the blades in the blade top, 50% of blade height and blade root along the streamline direction in the blade parameters, the theoretical annular quantity difference value of the inlet and outlet of the blades, the number of the blades, the radial runner size of the impeller, the design point flow, the design rotating speed, the impeller inclination angle at the tail edge and the enthalpy difference load of the blades at all positions along the streamline direction are calculated;
according to the three-dimensional reverse design theory of compressible fluid aiming at mixed flow and radial impellers, based on a mass conservation equation, according to the input design point flow, design rotating speed, impeller inclination angle at the tail edge, the number of blades and impeller meridian runner size under the standard condition, the relative speed distribution of the upper surface and the lower surface of the blades is solved under a rotating coordinate system, and according to the relative speed distribution, the enthalpy difference load of the blades at all positions along the streamline direction is solved by combining the load distribution of the blades at the blade top, 50% of blade height and the blade root along the streamline direction and the theoretical annular quantity difference of the blade inlet and outlet.
A2: determining the surface speed distribution of the blade according to enthalpy difference loads at various positions of the blade along the streamline direction;
The enthalpy difference between the pressure surface and the suction surface of the blade can be converted into bound vortex (bound vortex) of the surface of the blade, and the intensity of the bound vortex of the surface of the blade depends on the speed distribution of the surface of the blade according to the kelvin theory, so that the speed distribution of the surface of the blade can be obtained.
A3: the blade shape is determined from the blade surface velocity profile.
According to the theory of fluid flow along a curved surface, the velocity distribution of the blade surface depends on the curvature of the blade, so as to determine the shape of the blade, and this design method is called an inverse design method.
The invention is not limited specifically, as long as the corresponding function can be realized, and the invention is not limited specifically.
The embodiment provides an alternative implementation manner of S110, which specifically includes the following steps:
b1: if the surge flow represented by the second performance curve is smaller than the target surge flow in the second preset performance requirement, adjusting the position of the point A so as to reduce the axial distance between the point O of the inlet of the blade tip and the point A, obtaining an adjusted geometric model of the widened flow groove, and returning to the step S109;
B2: if the axial distance between the O point and the a point reaches the minimum value, the second performance curve still does not meet the second preset performance requirement, DP0b is reduced, and S103 is executed back until the second performance curve meets the second preset performance requirement, so as to complete the joint design of the widened flow groove and the impeller.
B3: if the surge flow represented by the second performance curve is greater than the target surge flow in the second preset performance requirement, adjusting the position of the point A to increase the axial distance between the point O and the point A of the top inlet position of the blade, obtaining an adjusted geometric model of the widened flow groove, and returning to the step S109;
b4: if the axial distance between the O point and the a point reaches the maximum value, the second performance curve still does not meet the second preset performance requirement, DP0b is increased, and S103 is executed back until the second performance curve meets the second preset performance requirement, so as to complete the joint design of the widened flow groove and the impeller.
Wherein, the value range of L-a is as follows: [ 0.03X impeller axial length, 0.05X impeller axial length ], the positions of the O point and the X point are fixed, and the axial distance between the O point and the X point is represented by L-X, so that the value of the axial distance between the O point and the A point is in the range of [ 0.03X impeller axial length+L-X, 0.05X impeller axial length+L-X ].
The method for adjusting the blade load DP0b from the inlet position O point of the blade top to the slotting position A point of the widened flow slot is as follows:
referring to fig. 7, the X axis is the dimensionless meridian length, the O point is the top inlet position, 1 is the top outlet position, X is the large blade roar spatial position, and a is the slot position of the widened flow slot. The curve is the derivative value of the blade surface speed vortex quantity and meridian length at different positions along the streamline direction, namely the integral area of the curve is the annular quantity difference value (defined and fixed before) of the blade inlet and outlet.
The blade load DP0b from the point O to the point A, namely the area surrounded by the curve from the point O to the point A and the X axis, can obviously improve the surge flow by increasing the area, and the control of the curve has 4 parameters: o_ Y, N1, N2 and slope.
Wherein O_Y is the Y coordinate of the curve corresponding to the X-axis 0 point, N1 is a number of 0-1, N2 is a number of 0-1, N1 is smaller than N2, and the slope is the slope of the curve line segment before N1 and N2, and can be positive or negative.
In order to improve the blade load DP0b from point O to point a, it is necessary to readjust the four parameters at the control blade tip, and in order to control the impeller performance without a large change in performance other than the surge region, it is proposed to adjust only the slope value, the smaller the slope value, the larger the DP0b, thereby increasing the surge margin.
Based on the above embodiment, the present embodiment correspondingly discloses a combined design device for widening a flow groove and an impeller, referring to fig. 8, the device includes:
a meridian flow channel determining unit 801, configured to determine a size of an impeller meridian flow channel according to an initial geometric parameter of the impeller;
a blade parameter setting unit 802 for setting blade parameters of the impeller;
a blade shape determining unit 803 for determining a blade shape from the blade parameters;
an impeller model determining unit 804, configured to determine a geometric model of the impeller according to the size of the meridian flow passage of the impeller, the blade parameters, and the blade shape;
a first simulation unit 805, configured to simulate a geometric model of the impeller, to obtain a first performance curve of the impeller;
a first parameter adjustment unit 806, configured to adjust the blade parameter and trigger the blade shape determination unit 803 if the first performance curve does not meet a first preset performance requirement;
a flow tank model determining unit 807, configured to determine geometric parameters of the widened flow tank if the first performance curve meets a first preset performance requirement, to obtain a geometric model of the widened flow tank, where the geometric parameters of the widened flow tank at least include a position of a slotting position a;
The second simulation unit 808 is configured to perform joint simulation on the geometric model of the impeller and the geometric model of the widened flow groove, so as to obtain a second performance curve of the impeller;
and a second parameter adjusting unit 809, configured to adjust the position of the point a and/or the blade load DP0b from the position O of the blade top inlet to the position a of the slot of the widened flow slot if the second performance curve does not meet the second preset performance requirement, and trigger the blade shape determining unit 803 or the second simulation unit 808 after modifying the corresponding geometric model according to the adjusted parameter until the second performance curve meets the second preset performance requirement, thereby completing the joint design of the widened flow slot and the impeller.
In some embodiments, the blade shape determining unit 803 is specifically configured to calculate the enthalpy difference load at each position along the streamline direction of the blade according to the load distribution along the streamline direction of the blade at the blade tip, 50% of the blade height and the blade root, the theoretical annular difference value of the blade inlet and outlet, the number of blades, the radial runner size of the impeller, the design point flow, the design rotation speed, the impeller inclination angle at the trailing edge in the blade parameters; determining the surface speed distribution of the blade according to enthalpy difference loads at various positions of the blade along the streamline direction; the blade shape is determined from the blade surface velocity profile.
In some embodiments, the first parameter adjustment unit 806 is specifically configured to increase the load at a critical position in the load distribution of the blade along the streamline direction in the blade parameter if the first performance curve indicates that the surge flow is smaller than the target surge flow in the first preset performance requirement, and decrease the load at the critical position if the first performance curve indicates that the surge flow is greater than the target surge flow in the first preset performance requirement; and if the first performance curve represents that the blocking allowance is smaller than the target blocking allowance in the first preset performance requirement, increasing the flow of the design point in the blade parameter.
In some embodiments, the second parameter adjustment unit 809 is specifically configured to:
if the surge flow represented by the second performance curve is smaller than the target surge flow in the second preset performance requirement, adjusting the position of the point A so as to reduce the axial distance between the point O and the point A, obtaining an adjusted geometric model of the widened flow groove, and triggering the second simulation unit;
if the axial distance between the O point and the A point reaches the minimum value, the second performance curve still does not meet the second preset performance requirement, the DP0b is reduced, the blade shape determining unit is triggered until the second performance curve meets the second preset performance requirement, and the combined design of the widened flow groove and the impeller is completed.
In some embodiments, the second parameter adjustment unit 809 is further specifically configured to:
if the surge flow represented by the second performance curve is larger than the target surge flow in the second preset performance requirement, adjusting the position of the point A so as to increase the axial distance between the point O and the point A, obtaining an adjusted geometric model of the widened flow groove, and triggering the second simulation unit;
if the axial distance between the O point and the A point reaches the maximum value, the second performance curve still does not meet the second preset performance requirement, the DP0b is increased, the blade shape determining unit is triggered until the second performance curve meets the second preset performance requirement, and the combined design of the widened flow groove and the impeller is completed.
The combined design device for widening the flow slot and the impeller disclosed by the embodiment determines the blade load DP0b from the position O of the blade top inlet to the position A of the opening of the widened flow slot and the position A of the opening of the widened flow slot according to the surge mechanism, and the two key control factors are surge flow. After the blade parameters are set, determining a geometric model of the impeller, simulating the geometric model of the impeller, if a first performance curve of the impeller obtained through simulation does not meet a first preset performance requirement, adjusting the blade parameters until the first performance curve of the impeller obtained through simulation meets the first preset performance requirement, determining geometric parameters of a widened flow groove comprising the position of a point A, obtaining the geometric model of the widened flow groove, then carrying out joint simulation on the geometric model of the impeller and the geometric model of the widened flow groove, if a second performance curve of the impeller obtained through simulation does not meet a second preset performance requirement, adjusting the position of the point A and/or DP0b, modifying the corresponding geometric model according to the adjusted parameters, and then carrying out simulation until the second performance curve meets the second preset performance requirement, completing joint design of the widened flow groove and the impeller, and obviously improving the effect of the widened flow while reducing design time and guaranteeing the efficiency of the impeller.
In the present specification, each embodiment is described in a progressive manner, and each embodiment is mainly described in a different point from other embodiments, and identical and similar parts between the embodiments are all enough to refer to each other. For the device disclosed in the embodiment, since it corresponds to the method disclosed in the embodiment, the description is relatively simple, and the relevant points refer to the description of the method section.
It is further noted that relational terms such as first and second, and the like are 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. Moreover, 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 one … …" does not exclude the presence of other like elements in a process, method, article, or apparatus that comprises the element.
The steps of a method or algorithm described in connection with the embodiments disclosed herein may be embodied directly in hardware, in a software module executed by a processor, or in a combination of the two. The software modules may be disposed in random access memory RAM, memory, read only memory ROM, electrically programmable ROM, electrically erasable programmable ROM, registers, hard disk, a removable disk, a CD-ROM, or any other form of storage medium known in the art.
The above embodiments may be combined in any manner, and features described in the embodiments in the present specification may be replaced or combined with each other in the above description of the disclosed embodiments, so as to enable one skilled in the art to make or use the present application.
The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the invention. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (10)
1. The combined design method for widening the flow groove and the impeller is characterized by comprising the following steps of:
determining the size of a meridian runner of the impeller according to the initial geometric parameters of the impeller;
setting blade parameters of an impeller;
determining a blade shape according to the blade parameters;
determining a geometric model of the impeller according to the size of the radial flow channel of the impeller, the blade parameters and the blade shape;
simulating a geometric model of the impeller to obtain a first performance curve of the impeller;
if the first performance curve does not meet the first preset performance requirement, adjusting the blade parameters, and returning to execute the step of determining the blade shape according to the blade parameters;
if the first performance curve meets a first preset performance requirement, determining the geometric parameters of the widened flow grooves, and obtaining a geometric model of the widened flow grooves, wherein the geometric parameters of the widened flow grooves at least comprise the positions of the A points of the slotting positions;
performing joint simulation on the geometric model of the impeller and the geometric model of the widened flow groove to obtain a second performance curve of the impeller;
and if the second performance curve does not meet the second preset performance requirement, adjusting the position of the point A and/or the blade load DP0b from the position O of the blade top inlet to the position A of the slotting position of the widened flow channel, modifying the corresponding geometric model according to the adjusted parameters, and then simulating until the second performance curve meets the second preset performance requirement, thereby completing the joint design of the widened flow channel and the impeller.
2. The method of claim 1, wherein said determining a blade shape from said blade parameters comprises:
according to the load distribution of the blades at the blade top, 50% of blade height and blade root along the streamline direction in the blade parameters, the theoretical annular difference value of the inlet and outlet of the blades, the number of the blades, the radial flow channel size of the impeller, the design point flow, the design rotating speed, the inclination angle of the impeller at the tail edge and the enthalpy difference load of the blades at all positions along the streamline direction are calculated;
determining the surface speed distribution of the blade according to enthalpy difference loads at various positions of the blade along the streamline direction;
the blade shape is determined from the blade surface velocity profile.
3. The method of claim 1, wherein said adjusting said blade parameter comprises:
if the first performance curve represents that the surge flow is smaller than the target surge flow in the first preset performance requirement, increasing the load of a key position in the load distribution of the blade along the streamline direction in the blade parameter;
if the first performance curve represents that the surge flow is larger than the target surge flow in the first preset performance requirement, reducing the load of the key position;
and if the first performance curve represents that the blocking allowance is smaller than the target blocking allowance in the first preset performance requirement, increasing the flow of the design point in the blade parameter.
4. The method according to claim 1, wherein adjusting the position of the point a and/or the blade load DP0b from the point O of the blade tip inlet to the point a of the slot opening position of the widened flow slot, and modifying the corresponding geometric model according to the adjusted parameters, and then performing simulation, comprises:
if the surge flow represented by the second performance curve is smaller than the target surge flow in the second preset performance requirement, adjusting the position of the point A to reduce the axial distance between the point O and the point A, obtaining an adjusted geometric model of the widened flow groove, and returning to execute the step of carrying out joint simulation on the geometric model of the impeller and the geometric model of the widened flow groove;
if the axial distance between the O point and the A point reaches the minimum value, the second performance curve still does not meet the second preset performance requirement, the DP0b is reduced, and the step of determining the shape of the blade according to the blade parameter is performed again until the second performance curve meets the second preset performance requirement, so that the joint design of the widened flow groove and the impeller is completed.
5. The method according to claim 4, wherein the adjusting the position of the point a and/or the blade load DP0b from the point O of the inlet of the blade tip to the point a of the slot position of the widened flow slot, and modifying the corresponding geometric model according to the adjusted parameters, and then performing simulation, further comprises:
If the surge flow represented by the second performance curve is larger than the target surge flow in the second preset performance requirement, adjusting the position of the point A to increase the axial distance between the point O and the point A, obtaining an adjusted geometric model of the widened flow groove, and returning to execute the step of carrying out joint simulation on the geometric model of the impeller and the geometric model of the widened flow groove;
if the axial distance between the O point and the A point reaches the maximum value, the second performance curve still does not meet the second preset performance requirement, the DP0b is increased, and the step of determining the shape of the blade according to the blade parameter is performed again until the second performance curve meets the second preset performance requirement, so that the combined design of the widened flow groove and the impeller is completed.
6. A combined design device for widening a flow channel and an impeller, comprising:
the meridian flow passage determining unit is used for determining the size of the meridian flow passage of the impeller according to the initial geometric parameters of the impeller;
a blade parameter setting unit for setting blade parameters of the impeller;
a blade shape determining unit for determining a blade shape according to the blade parameter;
the impeller model determining unit is used for determining a geometric model of the impeller according to the size of the radial flow channel of the impeller, the blade parameters and the blade shape;
The first simulation unit is used for simulating the geometric model of the impeller to obtain a first performance curve of the impeller;
the first parameter adjusting unit is used for adjusting the blade parameters and triggering the blade shape determining unit if the first performance curve does not meet a first preset performance requirement;
the flow groove model determining unit is used for determining the geometric parameters of the widened flow groove if the first performance curve meets a first preset performance requirement to obtain a geometric model of the widened flow groove, wherein the geometric parameters of the widened flow groove at least comprise the position of a slotting position A;
the second simulation unit is used for carrying out joint simulation on the geometric model of the impeller and the geometric model of the widened flow groove to obtain a second performance curve of the impeller;
and the second parameter adjusting unit is used for adjusting the blade load DP0b from the position of the point A and/or the position O of the blade top inlet to the position A of the slotting of the widened flow groove if the second performance curve does not meet the second preset performance requirement, and triggering the blade shape determining unit or the second simulation unit after modifying the corresponding geometric model according to the adjusted parameters until the second performance curve meets the second preset performance requirement, so as to complete the joint design of the widened flow groove and the impeller.
7. The device according to claim 6, wherein the blade shape determining unit is specifically configured to calculate enthalpy difference loads at various positions along the streamline direction of the blade according to load distribution of the blade along the streamline direction at the tip, 50% of blade height, and the root of the blade in the blade parameters, theoretical annular difference values of the inlet and the outlet of the blade, number of blades, radial runner size of the impeller, design point flow, design rotational speed, and impeller inclination angle at the trailing edge; determining the surface speed distribution of the blade according to enthalpy difference loads at various positions of the blade along the streamline direction; the blade shape is determined from the blade surface velocity profile.
8. The apparatus of claim 6, wherein the first parameter adjustment unit is specifically configured to increase a load at a critical location in a load distribution of the blade in the blade parameter along the streamline direction if the first performance curve represents a surge flow that is less than a target surge flow in a first preset performance requirement, and decrease the load at the critical location if the first performance curve represents a surge flow that is greater than the target surge flow in the first preset performance requirement; and if the first performance curve represents that the blocking allowance is smaller than the target blocking allowance in the first preset performance requirement, increasing the flow of the design point in the blade parameter.
9. The apparatus according to claim 6, wherein the second parameter adjustment unit is specifically configured to:
if the surge flow represented by the second performance curve is smaller than the target surge flow in the second preset performance requirement, adjusting the position of the point A so as to reduce the axial distance between the point O and the point A, obtaining an adjusted geometric model of the widened flow groove, and triggering the second simulation unit;
if the axial distance between the O point and the A point reaches the minimum value, the second performance curve still does not meet the second preset performance requirement, the DP0b is reduced, the blade shape determining unit is triggered until the second performance curve meets the second preset performance requirement, and the combined design of the widened flow groove and the impeller is completed.
10. The apparatus according to claim 9, wherein the second parameter adjustment unit is further specifically configured to:
if the surge flow represented by the second performance curve is larger than the target surge flow in the second preset performance requirement, adjusting the position of the point A so as to increase the axial distance between the point O and the point A, obtaining an adjusted geometric model of the widened flow groove, and triggering the second simulation unit;
If the axial distance between the O point and the A point reaches the maximum value, the second performance curve still does not meet the second preset performance requirement, the DP0b is increased, the blade shape determining unit is triggered until the second performance curve meets the second preset performance requirement, and the combined design of the widened flow groove and the impeller is completed.
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