Load-controllable vane and guide vane combined manufacturing method and vane pump

Abstract

The invention discloses a load-controllable vane and guide vane combined manufacturing method and a vane pump. Wherein the vane pump comprises vanes and guide vanes; the blade is provided with an upper crown side connected with the upper cover plate and a lower ring side connected with the lower cover plate, and two opposite ends of the blade are a blade inlet end and a blade outlet end respectively; the guide vane is arranged at the vane outlet end, the two opposite ends of the guide vane are the guide vane inlet end and the guide vane outlet end respectively, and the guide vane inlet end is adjacent to the vane outlet end. The guide vane is provided with an upper annular plate side connected with the upper annular plate and a lower annular plate side connected with the lower annular plate; the distribution rule of the velocity moments of the blades and the guide vanes along the axial surface streamline conforms to a preset function. The vane pump is long in service life and high in overall efficiency.

Description

Technical Field

[0001] The invention relates to the technical field of vane pumps, and in particular to a method for jointly manufacturing load-controllable vanes and guide vanes and a vane pump. Background Art

[0002] As the most widely used general machinery in all walks of life, vane pumps are not only used in industrial and agricultural fields such as petroleum, chemical industry, water conservancy, irrigation, but also in national strategic projects such as the Three Gorges Hydropower Station and nuclear power plants, and even in cutting-edge technology fields such as submarines, ships, and aerospace. According to statistics, the oil consumption of pumps accounts for about 5% of the total oil consumption in the country, and the power consumption accounts for about 20% of the total power generation in the country, and in the petroleum and chemical industries, it is as high as 59% and 26% respectively. my country vigorously advocates energy conservation and emission reduction and building a conservation-oriented society, so it is of great significance to optimize the design of the impeller of the vane pump to improve its hydraulic characteristics.

[0003] However, the existing vane pump has unreasonable design of impeller and guide vane, which leads to uneven distribution of load on the blades caused by the fluid after the fluid enters the impeller. The impeller and guide vane are designed separately, and the impeller and guide vane are not well matched. The flow interaction between the impeller and the guide vane is large, and the blade outlet loss is large, which affects the hydraulic and cavitation characteristics of the impeller pump, thereby reducing the service life of the blades and the efficiency of the device. Summary of the invention

[0004] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, one object of the present invention is to provide a vane pump with a long service life and high overall efficiency.

[0005] A vane pump according to an embodiment of the present invention comprises:

[0006] A blade, wherein the blade is disposed between an upper cover plate and a lower cover plate and together with the upper cover plate and the lower cover plate constitutes an impeller; the blade has an upper crown side connected to the upper cover plate and a lower ring side connected to the lower cover plate, and opposite ends of the blade are a blade inlet end and a blade outlet end respectively;

[0007] A guide vane, wherein the guide vane is arranged at the outlet end of the blade, and the opposite ends of the guide vane are respectively a guide vane inlet end and a guide vane outlet end, and the guide vane inlet end and the blade outlet end are adjacent; the guide vane is arranged between an upper ring plate and a lower ring plate, and the guide vane has an upper ring plate side connected to the upper ring plate and a lower ring plate side of the lower ring plate; the distribution law of the velocity moment of the blade and the guide vane along the axial streamline conforms to a preset function.

[0008] Compared with the traditional vane pump, the vane pump in the embodiment of the present invention can make the blade load distribution of the impeller more uniform, the blades and guide vanes cooperate better, and the water flow out of the blades can be smoother, reducing the hydraulic pulsation and impact at the blade outlet end and the resistance in the guide vane area, thereby improving the hydraulic and cavitation characteristics of the vane pump, thereby extending the service life of the vane pump and improving the overall efficiency of the vane pump.

[0009] In some embodiments, the preset function of the distribution law of the velocity moment of the blade along the axial streamline is:

[0010] C u r=C u1 r1+(C u2 r2-C u1 r1)·F1(x),

[0011] Among them, C u1 r1 is the velocity moment of the axial streamline at the blade inlet end, C u2 r2 is the velocity moment of the axial streamline at the blade outlet end, F1(x) is a dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the blade area, and x corresponds to the ratio between the length along the axial streamline between the predetermined position on the axial streamline and the blade inlet end and the total length of the axial streamline.

[0012] In some embodiments, the dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the blade area is:

[0013] F1(x)=a3·x 3 +a2·x 2 +a1·x+a0,

[0014] Among them, a3, a2, a1, and a0 are all given constants.

[0015] In some embodiments, the preset function of the distribution law of the velocity moment of the guide vane along the axial streamline is:

[0016] C u r=C u3 r3+(C u4 r4-C u3 r3)·F2(x),

[0017] Among them, C u3 r3 is the velocity moment of the axial streamline at the guide vane inlet end, C u4r4 is the velocity moment of the axial streamline at the guide vane outlet end, F2(x) is a dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the guide vane area, and x corresponds to the ratio between the length along the axial streamline between the predetermined position on the axial streamline and the blade inlet end and the total length of the axial streamline.

[0018] In some embodiments, the dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at each location in the guide vane area is:

[0019] F2(x)=b3·x 3 +b2·x 2 +b1·x+b0,

[0020] Among them, b3, b2, b1, and b0 are all given constants.

[0021] In some embodiments, the velocity moment at the blade outlet end is equal to the velocity moment at the guide vane inlet end.

[0022] The present invention also proposes a method for jointly manufacturing load-controllable blades and guide vanes.

[0023] According to the combined manufacturing method of the blade and guide vane with controllable load according to the embodiment of the present invention, wherein the blade and the guide vane are respectively the blade and the guide vane in the vane pump according to the embodiment of the present invention, the combined manufacturing method comprises:

[0024] Determine the velocity moment of the blade inlet end, the velocity moment of the blade outlet end, and the dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the blade area on at least two axial streamlines on the blade in the direction from the upper crown side to the lower ring side according to the use requirements of the impeller, so as to determine the shape of the blade;

[0025] Determine, according to the use requirements of the guide vane, a dimensionless cubic polynomial function of the velocity moment at the guide vane inlet end, the velocity moment at the guide vane outlet end, and the distribution law of the velocity moment at each location of the guide vane area on the axial streamlines on at least two axial streamlines in the direction from the upper ring plate side to the lower ring plate side of the guide vane, so as to determine the shape of the guide vane;

[0026] The axial streamlines at other positions on the impeller and the guide vane are determined by interpolation method based on at least two of the axial streamlines, so as to manufacture blades and guide vanes of predetermined shapes.

[0027] The blades and guide vanes obtained by the combined manufacturing method of blades and guide vanes with controllable loads in the embodiment of the present invention can make the blade load distribution more uniform, the blades and guide vanes cooperate better, and the water flow out of the blades can be smoother, reducing the hydraulic pulsation and impact at the blade outlet end, reducing the resistance in the guide vane area, and thus improving the hydraulic and cavitation characteristics of the vane pump, thereby extending the service life of the vane pump and improving the overall efficiency of the vane pump.

[0028] In some embodiments, the distribution law of the velocity moment at the inlet end of the blade and the velocity moment at the outlet end of the blade along the axial streamline conforms to a preset function, and the preset function of the distribution law of the velocity moment of the blade along the axial streamline is: C u r=C u1 r1+(C u2 r2-C u1 r1)·F1(x),

[0029] Among them, C u3 r3 is the velocity moment of the axial streamline at the guide vane inlet end, C u4 r4 is the velocity moment of the axial streamline at the guide vane outlet end, F2(x) is a dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the guide vane area, and x corresponds to the ratio between the length along the axial streamline between the predetermined position on the axial streamline and the blade inlet end and the total length of the axial streamline.

[0030] In some embodiments, the dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the blade area is:

[0031] F1(x)=a3·x 3 +a2·x 2 +a1·x+a0,

[0032] Among them, a3, a2, a1, and a0 are all given constants.

[0033] In some embodiments, the preset function of the distribution law of the velocity moment of the guide vane along the axial streamline is:

[0034] C u r=C u3 r3+(C u4 r4-C u3 r3)·F2(x),

[0035] Among them, C u3 r3 is the velocity moment of the axial streamline at the guide vane inlet end, C u4r4 is the velocity moment of the axial streamline at the guide vane outlet end, F2(x) is a dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the guide vane area, and x corresponds to the ratio between the length along the axial streamline between the predetermined position on the axial streamline and the blade inlet end and the total length of the axial streamline.

[0036] In some embodiments, the dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at each location in the guide vane area is:

[0037] F2(x)=b3·x 3 +b2·x 2 +b1·x+b0,

[0038] Among them, b3, b2, b1, and b0 are all given constants.

[0039] In some embodiments, at least two of the axial streamlines include the axial streamlines located on the upper crown side and the lower ring side of the blade region.

[0040] In some embodiments, at least two of the axial streamlines include the axial streamlines located on the upper ring plate side and the lower ring plate side of the guide vane region.

[0041] In some embodiments, the velocity moment at the blade outlet end is equal to the velocity moment at the guide vane inlet end.

[0042] In some embodiments, the interpolation method is a spline interpolation method, a Lagrange interpolation method, a Newton interpolation method, a Hermite interpolation method or a piecewise interpolation method.

[0043] Additional aspects and advantages of the present invention will be given in part in the following description and in part will be obvious from the following description, or will be learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0044] The above and / or additional aspects and advantages of the present invention will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0045] Figure 1 A schematic diagram of the structure of a vane pump according to an embodiment of the present invention;

[0046] Figure 2 A schematic diagram of the structure of the blades and guide vanes of a vane pump according to an embodiment of the present invention;

[0047] Figure 3 A flowchart of a method for manufacturing blades and guide vanes of a vane pump according to an embodiment of the present invention;

[0048] Figure 4This is a schematic diagram of the relative velocity moment distribution of blades and guide vanes along the axial streamline length of the upper crown side and lower ring side of the blades, and the upper ring plate side and lower ring plate side of the guide vanes of the vane pump optimization design model according to an embodiment of the present invention.

[0049] Reference numerals:

[0050] Blade 1; upper crown side 11; lower ring side 12; blade inlet end 13; blade outlet end 14; upper cover plate 2; lower cover plate 3; guide vane 4; upper ring plate side 41; lower ring plate side 42; guide vane inlet end 43; guide vane outlet end 44; upper ring plate 5; lower ring plate 6. DETAILED DESCRIPTION

[0051] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0052] Combine the following Figure 1 to Figure 2 and Figure 4 A vane pump according to an embodiment of the present invention will be described.

[0053] like Figure 1 to Figure 2 and Figure 4 As shown, the vane pump according to the embodiment of the present invention includes a vane 1 and a guide vane 4 .

[0054] Among them, the blade 1 is arranged between the upper cover plate 2 and the lower cover plate 3 and together with the upper cover plate 2 and the lower cover plate 3 constitutes an impeller; the blade 1 has an upper crown side 11 connected to the upper cover plate 2 and a lower ring side 12 connected to the lower cover plate 3, and the opposite ends of the blade 1 are respectively a blade inlet end 13 and a blade outlet end 14.

[0055] The guide vane 4 is arranged at the blade outlet end 14, and the opposite ends of the guide vane 4 are respectively a guide vane inlet end 43 and a guide vane outlet end 44, and the guide vane inlet end 43 is adjacent to the blade outlet end 14; the guide vane 4 is arranged between the upper ring plate 5 and the lower ring plate 6, and the upper ring plate 5 and the lower ring plate 6 are respectively and correspondingly located at the outer periphery of the upper cover plate 2 and the lower cover plate 3, and the guide vane 4 has an upper ring plate side 41 connected to the upper ring plate 5 and a lower ring plate side 42 of the lower ring plate 6; the distribution law of the velocity moment of the blade 1 and the guide vane 4 along the axial streamline conforms to the preset function.

[0056] Compared with the traditional vane pump, the vane pump in the embodiment of the present invention can make the load distribution of the impeller blade 1 more uniform, and the blade 1 and the guide vane 4 cooperate better, so that the water flow out of the blade 1 can have a smoother transition, reduce the hydraulic pulsation and impact at the blade outlet end 14, and reduce the resistance in the guide vane 4 area, thereby improving the hydraulic and cavitation characteristics of the vane pump, thereby extending the service life of the vane pump and improving the overall efficiency of the vane pump.

[0057] Specifically, the preset function of the distribution law of the velocity moment of blade 1 along the axial streamline is:

[0058] C u r=C u1 r1+(C u2 r2-C u1 r1)·F1(x),

[0059] Among them, C u1 r1 is the velocity moment of the axial streamline at the blade inlet end 13, C u2 r2 is the velocity moment of the axial streamline at the blade outlet end 14, F1(x) is a dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the blade 1 region, and x corresponds to the ratio between the length along the axial streamline between the predetermined position on the axial streamline and the blade inlet end 13 and the total length of the axial streamline (that is, the total length is the length of the axial streamline from the blade inlet end 13 to the guide vane outlet end 44).

[0060] By reasonably giving C u1 r1, C u2 The value of r2, that is, the velocity moment at the blade inlet end 13 and the blade outlet end 14, is a predetermined value of the design. u1 r1, C u2 The value of r2 can be determined based on design experience or can be selected based on the numerical value in the vane pump impeller design manual.

[0061] The dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at each location in the blade area 1 is:

[0062] F1(x)=a3·x 3 +a2·x 2 +a1·x+a0,

[0063] Among them, a3, a2, a1, and a0 are all given constants.

[0064] By changing the given values ​​of a3, a2, a1, a0 and C u1 r1, C u2The predetermined value of r2 can change the variation law of the axial streamline velocity moment from the blade inlet end 13 to the blade outlet end 14, thereby affecting the shape of the blade 1.

[0065] The preset function of the distribution law of the velocity moment of the guide vane 4 along the axial streamline is:

[0066] C u r=C u3 r3+(C u4 r4-C u3 r3)·F2(x),

[0067] Among them, C u3 r3 is the velocity moment of the axial streamline at the guide vane inlet end 43, C u4 r4 is the velocity moment of the axial streamline at the guide vane outlet end 44, F2(x) is a dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the guide vane 4 region, and x corresponds to the ratio between the length along the axial streamline between the predetermined position on the axial streamline and the blade inlet end 13 and the total length of the axial streamline.

[0068] By reasonably giving C u3 r3, C u4 The value of r4, that is, the velocity moment at the guide vane inlet end 43 and the guide vane outlet end 44 is a predetermined value of the design. u3 r3, C u4 The value of r4 can be determined based on design experience or can be selected based on the numerical value in the vane pump impeller design manual.

[0069] The dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at each location in the guide vane 4 region is:

[0070] F2(x)=b3·x 3 +b2·x 2 +b1·x+b0,

[0071] Among them, b3, b2, b1, and b0 are all given constants.

[0072] By changing the given values ​​of b3, b2, b1, b0 and C u3 r3, C u4 The value of r4 can change the variation law of the axial streamline velocity moment from the guide vane inlet end 43 to the guide vane outlet end 44, thereby affecting the shape of the guide vane 4.

[0073] The velocity moment at the blade outlet 14 is equal to the velocity at the guide vane inlet 43, that is, C u2 r2=C u3 r3.

[0074] In summary, the distribution law of the velocity moment of the blades 1 and the guide vanes 4 in the vane pump of the embodiment of the present invention along the axial streamlines conforms to the preset function, which can make the load distribution of the blade 1 more uniform, and the blades 1 and the guide vanes 4 cooperate better, so that the water flow out of the blades 1 can have a smoother transition, reduce the hydraulic pulsation and impact at the blade outlet end 14, reduce the resistance of the guide vane 4 area, and thus improve the hydraulic and cavitation characteristics of the vane pump, thereby extending the service life of the vane pump and improving the efficiency of the device.

[0075] The invention also proposes a method for jointly manufacturing an impeller and a guide vane of a vane pump.

[0076] like Figures 1 to 4 As shown, according to the combined manufacturing method of the impeller and guide vane of the vane pump of the embodiment of the present invention, the blade 1 and the guide vane 4 are respectively the blade 1 and the guide vane 4 in the vane pump of the embodiment of the present invention; the combined manufacturing method comprises:

[0077] Determine the velocity moment C of the blade inlet end 13 on at least two axial streamlines on the blade 1 in the direction from the upper crown side 11 to the lower ring side 12 according to the use requirements of the impeller. u1 r1, velocity moment C at the blade outlet 14 u2 r2 and the dimensionless cubic polynomial function F1(x) of the distribution law of the velocity moment of the axial streamline at various locations in the blade 1 area to determine the shape of blade 1.

[0078] Determine the velocity moment C of the guide vane inlet end 43 on at least two axial streamlines on the guide vane 4 in the direction from the upper ring plate side 41 to the lower ring plate side 42 according to the use requirements of the guide vane 4. u3 r3, velocity moment C at the guide vane outlet 44 u4 r4 and the dimensionless cubic polynomial function F2(x) of the distribution law of the velocity moment of the axial streamline at various locations in the guide vane 4 area to determine the shape of the guide vane 4.

[0079] The axial streamlines at other positions on the impeller and the guide vane 4 are determined by interpolation method based on at least two axial streamlines, so as to manufacture the blades 1 and the guide vane 4 of predetermined shapes.

[0080] The blades and guide vanes 4 manufactured by the combined manufacturing method of the impeller and guide vanes of the vane pump in the embodiment of the present invention can make the load distribution of the blade 1 more uniform, and the blade 1 and the guide vane 4 cooperate better, so that the water flow out of the blade 1 can have a smoother transition, reduce the hydraulic pulsation and impact at the blade outlet end 14, reduce the resistance in the guide vane 4 area, and thus improve the hydraulic and cavitation characteristics of the vane pump, thereby extending the service life of the vane pump blade 1 and improving the efficiency of the device.

[0081] Specifically, at least two axial streamlines include an axial streamline from the upper crown side 11 located in the blade 1 area to the upper ring side located in the guide vane 4 area (the axial streamline includes Figure 4 The axial streamlines A at the upper crown side 11, the axial streamlines C at the upper ring plate side 41, and the axial streamlines located at the lower ring side 12 of the blade 1 area to the lower ring plate side 42 of the guide vane 4 area (the axial streamlines include the following: Figure 4 The axial streamline B at the lower ring side 12 and the axial streamline D at the lower ring plate side 42 are shown.

[0082] The distribution law of the velocity moment of the blade inlet end 13 and the velocity moment of the blade outlet end 14 along the axial streamline conforms to the preset function. The preset function of the distribution law of the velocity moment of the blade 1 along the axial streamline is: C u r=C u1 r1+(C u2 r2-C u1 r1)·F1(x),

[0083] Among them, C u1 r1 is the velocity moment of the axial streamline at the blade inlet end 13, C u2 r2 is the velocity moment of the axial streamline at the blade outlet end 14, F1(x) is a dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the blade 1 region, and x corresponds to the ratio between the length along the axial streamline between the predetermined position on the axial streamline and the blade inlet end 13 and the total length of the axial streamline.

[0084] By reasonably giving C u1 r1, C u2 The value of r2, that is, the velocity moment at the blade inlet end 13 and the blade outlet end 14, is a predetermined value of the design. u1 r1, C u2 The value of r2 can be determined based on design experience or can be selected based on the numerical value in the vane pump impeller design manual.

[0085] The dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at each location in the blade area 1 is:

[0086] F1(x)=a3·x 3 +a2·x 2 +a1·x+a0,

[0087] Among them, a3, a2, a1, and a0 are all given constants.

[0088] By changing the given values ​​of a3, a2, a1, a0 and C u1 r1, C u2 The predetermined value of r2 can change the variation law of the axial streamline velocity moment from the blade inlet end 13 to the blade outlet end 14, thereby affecting the shape of the blade 1.

[0089] The preset function of the distribution law of the velocity moment of the guide vane 4 along the axial streamline is:

[0090] C u r=C u3 r3+(C u4 r4-C u3 r3)·F2(x),

[0091] Among them, C u3 r3 is the velocity moment of the axial streamline at the guide vane inlet end 43, C u4 r4 is the velocity moment of the axial streamline at the guide vane outlet end 44, F2(x) is a dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the guide vane 4 region, and x corresponds to the ratio between the length along the axial streamline between the predetermined position on the axial streamline and the blade inlet end 13 and the total length of the axial streamline.

[0092] By reasonably giving C u3 r3, C u4 The value of r4, that is, the velocity moment at the guide vane inlet end 43 and the guide vane outlet end 44 is a predetermined value of the design. u3 r3, C u4 The value of r4 can be determined based on design experience or can be selected based on the numerical value in the vane pump impeller design manual.

[0093] The dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at each location in the guide vane 4 region is:

[0094] F2(x)=b3·x 3 +b2·x 2 +b1·x+b0,

[0095] Among them, b3, b2, b1, and b0 are all given constants.

[0096] By changing the given values ​​of b3, b2, b1, b0 and C u3 r3, C u4 The value of r4 can change the variation law of the axial streamline velocity moment from the guide vane inlet end 43 to the guide vane outlet end 44, thereby affecting the shape of the guide vane 4.

[0097] The velocity moment at the blade outlet 14 is equal to the velocity at the guide vane inlet 43, that is, C u2 r2=C u3 r3.

[0098] Furthermore, by optimizing the design, a3, a2, a1, a0, b3, b2, b1, b0, C u1 r1, C u2 r2, Cu3 r3, C u4 The 12 parameters r4 can change the variation law of the axial streamline velocity moment from the blade inlet end 13 to the guide vane outlet end 44, thereby affecting the shape of the blade 1 and the guide vane 4.

[0099] Optionally, the interpolation method is a spline interpolation method, a Lagrange interpolation method, a Newton interpolation method, a Hermite interpolation method or a piecewise interpolation method.

[0100] The following will be described through more specific embodiments and combined Figures 1 to 4 The manufacturing method of the impeller and guide vane 4 of the vane pump is further described.

[0101] First, according to the actual working condition of the impeller, determine the velocity moment C of the blade inlet end 13 of the axial streamline of the crown side 11 of the blade 1 u1 r 1上冠侧 , the velocity moment C at the blade outlet 14 u2 r 2上冠侧 The value of and the dimensionless cubic polynomial function F of the distribution law of the velocity moment of the axial streamline at each location in the blade 1 area 1上冠侧 (x) a 3上冠侧 、a 2上冠侧 、a 1上冠侧 、a 0上冠侧 The value of the blade inlet end 13 of the axial streamline of the lower ring side 12 is determined at the same time. u1 r 1下环侧 , the velocity moment C at the blade outlet 14 u2 r 2下环侧 The value of and the dimensionless cubic polynomial function F of the distribution law of the velocity moment of the axial streamline at each location in the blade 1 area 1下环侧 (x) a 3下环侧 、a 2下环侧 、a 1下环侧 、a 0下环侧 At the same time, determine the velocity moment C of the guide vane inlet end 43 of the axial streamline of the ring plate side 41 on the guide vane 4 u3 r 3上环板侧 , the velocity moment C at the guide vane outlet 44 u4 r 4上环板侧 The value of and the dimensionless cubic polynomial function F of the distribution law of the velocity moment of the axial streamline at each location in the guide vane 4 region 2上环板侧 (x) b 3上冠侧 、b 2上冠侧 、b 1上冠侧 、b 0上冠侧 The velocity moment C of the guide vane inlet end 43 of the axial streamline on the lower ring plate side 42 is determined at the same time. u3 r 3下环板侧 , the velocity moment C at the guide vane outlet 44u4 r 4下环板侧 The value of and the dimensionless cubic polynomial function F of the distribution law of the velocity moment of the axial streamline at each location in the guide vane 4 region 2下环板侧 (x) b 3下环板侧 、b 2下环板侧 、b 1下环板侧 、b 0下环板侧 The value of C is advantageously, for ease of production, u2 r 2上冠侧 -C u1 r 1上冠侧 =C u2 r 2下环侧 -C u1 r 1下环侧 , C u4 r 4上环板侧 -C u3 r 3上环板侧 =C u4 r 4下环板侧 -C u3 r 3下环板侧 , C u2 r 2上冠侧 =C u3 r 3上环板侧 , C u2 r 2下环侧 =C u3 r 3下环板侧 In this way, the velocity moments of the upper crown side 11 and the lower ring side 12 of the blade 1, and the velocity moments of the upper ring plate 5 and the lower ring plate 6 of the guide vane 4 are determined, and then the shapes of the blade 1 and the guide vane 4 are determined. It can be known that there are countless axial streamlines between the axial streamlines of the upper crown side 11 and the axial streamlines of the lower ring side 12, and there are countless axial streamlines between the axial streamlines of the upper ring plate side 41 and the axial streamlines of the lower ring plate side 42. These axial streamlines cannot be exhaustively enumerated, so the interpolation method can be used to determine the axial streamlines at other positions, so that the shapes of the blade 1 and the guide vane 4 are determined.

[0102] Of course, the above embodiments are merely illustrative and cannot be construed as limiting the scope of protection of the present invention. For example, any two or three or more axial streamlines between the upper crown axial streamline and the lower ring axial streamline, and between the upper ring plate 5 axial streamline and the lower ring plate 6 axial streamline may also be selected.

[0103] According to the manufacturing method of the impeller and guide vane 4 of the embodiment of the present invention, an impeller and guide vane 4 that satisfies a cubic polynomial function can be designed through the above steps. The manufacturing method of the impeller and guide vane 4 is simple in design and easy to implement. Applying the manufacturing method of the impeller and guide vane 4 to the parameter optimization design of the vane pump can make the load distribution of the blade 1 more uniform, the blade 1 and the guide vane 4 better matched, and the flow impact small, thereby improving the hydraulic and cavitation characteristics of the vane pump, and then extending the service life and efficiency of the vane pump.

[0104] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "illustrative embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0105] Although the embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. A vane pump, characterized in that: include: A blade, wherein the blade is disposed between an upper cover plate and a lower cover plate and together with the upper cover plate and the lower cover plate constitutes an impeller; the blade has an upper crown side connected to the upper cover plate and a lower ring side connected to the lower cover plate, and opposite ends of the blade are a blade inlet end and a blade outlet end respectively; A guide vane, wherein the guide vane is arranged at the outlet end of the blade, and the opposite ends of the guide vane are respectively a guide vane inlet end and a guide vane outlet end, and the guide vane inlet end and the blade outlet end are adjacent; the guide vane is arranged between an upper ring plate and a lower ring plate, and the guide vane has an upper ring plate side connected to the upper ring plate and a lower ring plate side of the lower ring plate; the distribution law of the velocity moment of the blade and the guide vane along the axial streamline conforms to a preset function.

2. The vane pump according to claim 1, characterized in that: The preset function of the distribution law of the velocity moment of the blade along the axial streamline is: C u r=C u1 r1+(C u2 r2-C u1 r1)·F1(x), Among them, C u1 r1 is the velocity moment of the axial streamline at the blade inlet end, C u2 r2 is the velocity moment of the axial streamline at the blade outlet end, F1(x) is a dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the blade area, and x corresponds to the ratio between the length along the axial streamline between the predetermined position on the axial streamline and the blade inlet end and the total length of the axial streamline.

3. The vane pump according to claim 2, characterized in that: The dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the blade area is: F1(x)=a3·x 3 +a2·x 2 +a1·x+a0, Among them, a3, a2, a1, and a0 are all given constants.

4. The vane pump according to any one of claims 1 to 3, characterized in that: The preset function of the distribution law of the velocity moment of the guide vane along the axial streamline is: C u r=C u3 r3+(C u4 r4-C u3 r3)·F2(x), Among them, C u3 r3 is the velocity moment of the axial streamline at the guide vane inlet end, C u4 r4 is the velocity moment of the axial streamline at the guide vane outlet end, F2(x) is a dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the guide vane area, and x corresponds to the ratio between the length along the axial streamline between the predetermined position on the axial streamline and the blade inlet end and the total length of the axial streamline.

5. The vane pump according to claim 4, characterized in that: The dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at each location in the guide vane area is: F2(x)=b3·x 3 +b2·x 2 +b1·x+b0, Among them, b3, b2, b1, and b0 are all given constants.

6. The vane pump according to claim 5, characterized in that: The velocity moment at the blade outlet end is equal to the velocity moment at the guide vane inlet end.

7. A method for jointly manufacturing load-controllable blades and guide vanes, characterized in that: The blades and the guide vanes are respectively the blades and the guide vanes in the vane pump according to any one of claims 1 to 6, and the joint manufacturing method comprises: Determine the velocity moment of the blade inlet end, the velocity moment of the blade outlet end, and the dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the blade area on at least two axial streamlines on the blade in the direction from the upper crown side to the lower ring side according to the use requirements of the impeller, so as to determine the shape of the blade; Determine, according to the use requirements of the guide vane, a dimensionless cubic polynomial function of the velocity moment at the guide vane inlet end, the velocity moment at the guide vane outlet end, and the distribution law of the velocity moment at each location of the guide vane area on the axial streamlines on at least two axial streamlines in the direction from the upper ring plate side to the lower ring plate side of the guide vane, so as to determine the shape of the guide vane; The axial streamlines at other positions on the impeller and the guide vane are determined by interpolation method based on at least two of the axial streamlines, so as to manufacture blades and guide vanes of predetermined shapes.

8. The method for jointly manufacturing load-controllable blades and guide vanes according to claim 7, characterized in that: The distribution law of the velocity moment at the inlet end of the blade and the velocity moment at the outlet end of the blade along the axial streamline conforms to a preset function, and the preset function of the distribution law of the velocity moment of the blade along the axial streamline is: C u r=C u1 r1+(C u2 r2-C u1 r1)·F1(x), Among them, C u3 r3 is the velocity moment of the axial streamline at the guide vane inlet end, C u4 r4 is the velocity moment of the axial streamline at the guide vane outlet end, F2(x) is a dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the guide vane area, and x corresponds to the ratio between the length along the axial streamline between the predetermined position on the axial streamline and the blade inlet end and the total length of the axial streamline.

9. The method for jointly manufacturing load-controllable blades and guide vanes according to claim 8, characterized in that: The dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the blade area is: F1(x)=a3·x 3 +a2·x 2 +a1·x+a0, Among them, a3, a2, a1, and a0 are all given constants.

10. The method for jointly manufacturing load-controllable blades and guide vanes according to any one of claims 7 to 9, characterized in that: The preset function of the distribution law of the velocity moment of the guide vane along the axial streamline is: C u r=C u3 r3+(C u4 r4-C u3 r3)·F2(x), Among them, C u3 r3 is the velocity moment of the axial streamline at the guide vane inlet end, C u4 r4 is the velocity moment of the axial streamline at the guide vane outlet end, F2(x) is a dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at various locations in the guide vane area, and x corresponds to the ratio between the length along the axial streamline between the predetermined position on the axial streamline and the blade inlet end and the total length of the axial streamline.

11. The method for jointly manufacturing load-controllable blades and guide vanes according to claim 10, characterized in that: The dimensionless cubic polynomial function of the distribution law of the velocity moment of the axial streamline at each location in the guide vane area is: F2(x)=b3·x 3 +b2·x 2 +b1·x+b0, Among them, b3, b2, b1, and b0 are all given constants.

12. The method for jointly manufacturing load-controllable blades and guide vanes according to claim 7, characterized in that: The at least two axial streamlines include the axial streamlines located on the upper crown side and the lower ring side of the blade area.

13. The method for jointly manufacturing load-controllable blades and guide vanes according to claim 7, characterized in that: The at least two axial surface streamlines include the axial surface streamlines located on the upper ring plate side and the lower ring plate side of the guide vane area.

14. The method for jointly manufacturing load-controllable blades and guide vanes according to claim 8, characterized in that: The velocity moment at the blade outlet end is equal to the velocity moment at the guide vane inlet end.

15. The method for jointly manufacturing load-controllable blades and guide vanes according to any one of claims 7 to 9, characterized in that: The interpolation method is a spline interpolation method, a Lagrange interpolation method, a Newton interpolation method, a Hermite interpolation method or a piecewise interpolation method.

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