Method for manufacturing a blade and a guide vane of a controllable load and a blade pump

Abstract

The application discloses a controllable load blade and guide vane combined manufacturing method and a blade pump. The blade pump comprises a blade and a guide vane; the blade has an upper crown side connected with an upper cover plate and a lower ring side connected with a lower cover plate, and opposite ends of the blade are a blade inlet end and a blade outlet end respectively; the guide vane is arranged at the blade outlet end, and opposite ends of the guide vane are a guide vane inlet end and a guide vane outlet end respectively, and the guide vane inlet end is adjacent to the blade outlet end; the guide vane has an upper ring plate side connected with an upper ring plate and a lower ring plate side connected with a lower ring plate; and the distribution law of the velocity moment of the blade and the guide vane along the axial surface streamline conforms to a preset function. The blade pump has a long service life and high overall efficiency.

Description

Technical Field

[0001] This invention relates to the field of vane pump technology, and in particular to a method for manufacturing a vane and guide vane with controllable load, and a vane pump. Background Technology

[0002] As the most widely used general-purpose machinery in various industries, vane pumps are not only used in industrial and agricultural fields such as petroleum, chemical, water conservancy, and irrigation, but also in national strategic projects such as the South-to-North Water Diversion Project, the Three Gorges Dam, and nuclear power plants, and even in cutting-edge technology fields such as submarines, ships, and aerospace.

[0003] However, existing impeller pumps suffer from uneven load distribution on the blades after the fluid enters the impeller due to unreasonable impeller and guide vane design. The impeller and guide vanes are designed separately, and the fit between the impeller and guide vanes is insufficient. The flow interaction between the impeller and guide vanes is large, resulting in large blade outlet losses. This 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 at least solve one of the technical problems existing in the prior art. Therefore, 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 includes:

[0006] The blade is disposed between the upper cover plate and the lower cover plate and together with the upper cover plate and the lower cover plate to form an impeller; the blade has an upper crown side that connects to the upper cover plate and a lower ring side that connects to the lower cover plate, and the opposite ends of the blade are the blade inlet end and the blade outlet end, respectively.

[0007] The guide vane is arranged at the blade exit end, with its two ends being the guide vane inlet end and the guide vane outlet end, respectively, and the guide vane inlet end and the blade exit end being adjacent to each other; the guide vane is disposed between the upper ring plate and the lower ring plate, and the guide vane has an upper ring plate side connecting the upper ring plate and a lower ring plate side connecting the lower ring plate; the velocity torque of the blade and the guide vane is distributed along the axial streamline according to a preset function.

[0008] Compared to traditional vane pumps, the vane pump of this invention, due to the fact that the velocity torque of the blades and guide vanes along the axial streamlines conforms to a preset function, can make the blade load distribution of the impeller more uniform, the blades and guide vanes better matched, and the water flow at the blade outlet can be smoother, reducing hydraulic pulsation and impact at the blade outlet end, reducing the resistance in the guide vane area, thereby improving the hydraulic and cavitation characteristics of the vane pump, and thus extending the service life of the vane pump and improving the overall efficiency of the vane pump.

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

[0010] C u r=C u1 r 1 +(C u2 r 2 -C u1 r 1 )·F 1 (x) ,

[0011] in, C u1 r 1 represents the velocity torque of the axial streamline at the blade inlet end. C u2 r 2 represents the velocity torque of the axial streamline at the blade exit end. F 1 （x） Let be a dimensionless cubic polynomial function representing the distribution of velocity moments of the axial streamlines at various points in the blade region. x The ratio between the predetermined position on the axial streamline and the length of the axial streamline between the blade inlet end and the total length of the axial streamline.

[0012] In some embodiments, the dimensionless cubic polynomial function representing the distribution of velocity moments of the axial streamlines at various points in the blade region is:

[0013] F 1 (x)=a 3 ·x 3 +a 2 ·x 2 +a 1 ·x+a 0,

[0014] in, a 3 、a 2 、a 1 、a 0 are all given constants.

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

[0016] C u r=C u3 r 3 +(C u4r 4 -C u3 r 3 )·F 2 (x) ,

[0017] in, C u3 r 3 represents the velocity torque of the axial streamline at the guide vane inlet end. C u4 r 4 represents the velocity torque of the streamlined axial surface at the guide vane exit end. F 2 （x） Let be a dimensionless cubic polynomial function representing the distribution law of the velocity moments of the axial streamlines at various points in the guide vane region. x The ratio between the predetermined position on the axial streamline and the length of the axial streamline between the blade inlet end and the total length of the axial streamline.

[0018] In some embodiments, the dimensionless cubic polynomial function representing the distribution of velocity moments of the axial streamlines at various points in the guide vane region is:

[0019] F 2 (x)= b 3 ·x 3 +b 2 ·x 2 +b 1 ·x+b 0,

[0020] in, b 3 、b 2 、b 1 、b 0 are all given constants.

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

[0022] This invention also proposes a method for the combined fabrication of blades and guide vanes with controllable loads.

[0023] According to an embodiment of the present invention, a method for jointly manufacturing a blade and a guide vane under controllable load, wherein the blade and the guide vane are respectively the blade and the guide vane in the blade pump of the present invention, and the method for jointly manufacturing includes:

[0024] Based on the impeller's usage requirements, determine the dimensionless cubic polynomial function of the velocity moments at the blade inlet end, the blade outlet end, and the distribution law of the velocity moments at various points in the blade region along at least two axial streamlines in the direction from the upper crown side to the lower ring side on the blade, in order to determine the shape of the blade;

[0025] Based on the usage requirements of the guide vane, determine the dimensionless cubic polynomial function of the velocity moment at the inlet end of the guide vane, the velocity moment at the outlet end of the guide vane, and the distribution law of the velocity moment at various points in the guide vane region on at least two axial streamlines on the guide vane in the direction from the upper ring plate side to the lower ring plate side, so as to determine the shape of the guide vane;

[0026] Based on at least two of the axial streamlines, interpolation is used to determine the axial streamlines at other locations on the impeller and guide vanes to produce blades and guide vanes of a predetermined shape.

[0027] The blades and guide vanes produced by the controllable load blade and guide vane joint manufacturing method of the present invention have blades and guide vanes that, because the distribution law of the velocity moment of the blades and guide vanes along the axial streamline conforms to the preset function, can make the blade load distribution more uniform, the blades and guide vanes better matched, can make the water flow at the blade exit more smoothly, reduce the hydraulic pulsation and impact at the blade outlet end, reduce the resistance in the guide vane area, and thus improve the hydraulic and cavitation characteristics of the blade pump, thereby extending the service life of the blade pump and improving the overall efficiency of the blade pump.

[0028] In some embodiments, the distribution patterns of the velocity moments at the blade inlet and outlet along the axial streamline conform to a preset function, and the preset function for the distribution patterns of the blade velocity moments along the axial streamline is: C u r=C u1 r 1 +(C u2 r 2 -C u1 r 1 )·F 1 (x) ,

[0029] in, C u3 r 3 represents the velocity torque of the axial streamline at the guide vane inlet end. C u4 r 4 represents the velocity torque of the streamlined axial surface at the guide vane exit end. F 2 （x）Let be a dimensionless cubic polynomial function representing the distribution law of the velocity moments of the axial streamlines at various points in the guide vane region. x The ratio between the predetermined position on the axial streamline and the length of the axial streamline between the blade inlet end and the total length of the axial streamline.

[0030] In some embodiments, the dimensionless cubic polynomial function representing the distribution of velocity moments of the axial streamlines at various points in the blade region is:

[0031] F 1 (x)=a 3 ·x 3 +a 2 ·x 2 +a 1 ·x+a 0,

[0032] in, a 3 、a 2 、a 1 、a 0 are all given constants.

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

[0034] C u r=C u3 r 3 +(C u4 r 4 -C u3 r 3 )·F 2 (x) ,

[0035] in, C u3 r 3 represents the velocity torque of the axial streamline at the guide vane inlet end. C u4 r 4 represents the velocity torque of the streamlined axial surface at the guide vane exit end. F 2 （x） Let be a dimensionless cubic polynomial function representing the distribution law of the velocity moments of the axial streamlines at various points in the guide vane region. x The ratio between the predetermined position on the axial streamline and the length of the axial streamline between the blade inlet end and the total length of the axial streamline.

[0036] In some embodiments, the dimensionless cubic polynomial function representing the distribution of velocity moments of the axial streamlines at various points in the guide vane region is:

[0037] F 2 (x)= b 3 ·x 3 +b 2 ·x 2 +b 1 ·x+b 0,

[0038] in, b 3 、b 2 、b 1 、b 0 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 annular plate side and the lower annular plate side of the guide vane region.

[0041] In some embodiments, the velocity torque at the blade exit end and the velocity torque at the guide vane inlet end are equal.

[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 invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

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

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

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

[0047] Figure 3 A flowchart illustrating 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 showing the relative velocity moment distribution of the blades and guide vanes along the streamline length of the axial plane on 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, in an optimized design model of a blade pump according to an embodiment of the present invention.

[0049] Figure label:

[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 Implementation

[0051] Embodiments of the present invention are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0052] The following is combined with Figures 1 to 2 and Figure 4 The vane pump of the present invention will be described in this embodiment.

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

[0054] The blade 1 is disposed 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 to form an impeller; the blade 1 has an upper crown side 11 that connects to the upper cover plate 2 and a lower ring side 12 that connects to the lower cover plate 3, and the two opposite ends of the blade 1 are the blade inlet end 13 and the blade outlet end 14, respectively.

[0055] Guide vane 4 is arranged at blade exit end 14. The two opposite ends of guide vane 4 are guide vane inlet end 43 and guide vane outlet end 44, respectively. Guide vane inlet end 43 and blade exit end 14 are adjacent to each other. Guide vane 4 is disposed between upper ring plate 5 and lower ring plate 6. Upper ring plate 5 and lower ring plate 6 are respectively located on the outer periphery of upper cover plate 2 and lower cover plate 3. Guide vane 4 has upper ring plate side 41 connecting upper ring plate 5 and lower ring plate side 42 connecting lower ring plate 6. The distribution law of velocity torque of blade 1 and guide vane 4 along the axial streamline conforms to the preset function.

[0056] Compared with traditional vane pumps, the vane pump of this invention has the advantage that the distribution of the velocity torque of the blades 1 and guide vanes 4 along the axial streamline conforms to a preset function, which makes the load distribution of the impeller blades 1 more uniform, the blades 1 and guide vanes 4 better matched, and the water flow at the blades 1 is smoother, reducing the hydraulic pulsation and impact at the blade outlet 14, reducing the resistance in the guide vane 4 area, thereby improving the hydraulic and cavitation characteristics of the vane pump, extending the service life of the vane pump and improving the overall efficiency of the vane pump.

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

[0058] C u r=C u1 r 1 +(C u2 r 2 -C u1 r 1 )·F 1 (x) ,

[0059] in, C u1 r 1 represents the velocity moment of the axial streamline at the blade inlet end 13. C u2 r 2 represents the velocity moment of the axial streamline at the blade exit end 14. F 1 （x） Let be a dimensionless cubic polynomial function representing the distribution of velocity moments along the axial streamlines in region 1 of the blade. x The ratio between the predetermined position on the axial streamline and the length of the axial streamline between the blade inlet end 13 and the total length of the axial streamline (i.e., the total length of the axial streamline from the blade inlet end 13 to the guide vane outlet end 44).

[0060] By giving reasonable C u1 r 1 、C u2 r The value of 2, that is, the velocity torque at the blade inlet end 13 and the blade outlet end 14, is the predetermined value of the design. C u1 r 1 、C u2 r The value of 2 can be determined based on design experience or by selecting values ​​from the impeller design manual for vane pumps.

[0061] The dimensionless cubic polynomial function representing the distribution of velocity moments along the axial streamlines in region 1 of the blade is:

[0062] F 1 (x)=a 3 ·x 3 +a 2 ·x 2 +a 1 ·x+a 0,

[0063] in, a 3 、a 2 、a 1 、a 0 are all given constants.

[0064] By changing a 3 、a 2 、a 1 、a The given value of 0 and C u1 r 1 、C u2 r The predetermined value of 2 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 blade 1.

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

[0066] C u r=C u3 r 3 +(C u4 r 4 -C u3 r 3 )·F 2 (x) ,

[0067] in, C u3 r 3 represents the velocity moment of the axial streamline at the guide vane inlet end 43. C u4 r 4 represents the velocity moment of the axial streamline at the guide vane exit end 44. F 2 （x） Let be a dimensionless cubic polynomial function representing the distribution of velocity moments of the axial streamlines at various points in region 4 of the guide vane. xThe ratio between the length of the axial streamline and the blade inlet end 13 at the predetermined position on the axial streamline and the total length of the axial streamline.

[0068] By giving reasonable C u3 r 3 、C u4 r The value of 4, that is, the velocity torque at the guide vane inlet end 43 and the guide vane outlet end 44, is the predetermined value of the design. C u3 r 3 、C u4 r The value of 4 can be determined based on design experience or by selecting values ​​from the impeller design manual for vane pumps.

[0069] The dimensionless cubic polynomial function representing the distribution of velocity moments along the axial streamlines in region 4 of the guide vane is:

[0070] F 2 (x)= b 3 ·x 3 +b 2 ·x 2 +b 1 ·x+b 0,

[0071] in, b 3 、b 2 、b 1 、b 0 are all given constants.

[0072] By changing b 3 、b 2 、b 1 、b The given value of 0 and C u3 r 3 、C u4 r The value of 4 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 torque at the blade exit end 14 is equal to the velocity at the guide vane inlet end 43, that is... C u2 r 2= C u3 r 3.

[0074] In summary, the velocity torque distribution of the blades 1 and guide vanes 4 along the axial streamline of the vane pump in this embodiment of the invention conforms to a preset function, which can make the load distribution of the blades 1 more uniform, the blades 1 and guide vanes 4 better coordinated, and the water flow at the blades 1 can be smoother, reducing the hydraulic pulsation and impact at the blade outlet end 14, reducing the resistance in the guide vane 4 area, thereby improving the hydraulic and cavitation characteristics of the vane pump, thus extending the service life of the vane pump and improving the efficiency of the device.

[0075] This invention also proposes a method for jointly manufacturing the impeller and guide vanes of a vane pump.

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

[0077] Determine the velocity torque at the blade inlet end 13 on at least two axial streamlines along the direction from the upper crown side 11 to the lower ring side 12 on blade 1, based on the impeller's usage requirements. C u1 r 1. Velocity torque at blade exit end 14 C u2 r 2. The dimensionless cubic polynomial function F1(x) is used to determine the shape of blade 1, along with the distribution law of the velocity moment of the axial streamline at various locations in region 1 of the blade.

[0078] Based on the usage requirements of the guide vane 4, determine the velocity torque of the guide vane inlet end 43 on at least two axial streamlines along the direction from the upper ring plate side 41 to the lower ring plate side 42 on the guide vane 4. C u3 r 3. The velocity torque at the guide vane outlet end 44 C u4 r 4. The dimensionless cubic polynomial function F2(x) is used to determine the distribution law of the velocity moment of the axial streamline at various points in the guide vane 4 region, so as to determine the shape of the guide vane 4.

[0079] Based on at least two axial streamlines, the axial streamlines at other positions on the impeller and guide vane 4 are determined by interpolation to produce blades 1 and guide vane 4 of a predetermined shape.

[0080] The blades and guide vanes 4 manufactured by the impeller and guide vane joint manufacturing method of the vane pump in this embodiment of the invention have a more uniform load distribution on the blades 1 and guide vanes 4 because the distribution law of the velocity torque of the blades 1 and guide vanes 4 along the axial streamline conforms to the preset function. This results in better coordination between the blades 1 and guide vanes 4, making the water flow at the blades 1 smoother, reducing hydraulic pulsation and impact at the blade outlet 14, reducing the resistance in the guide vane 4 area, thereby improving the hydraulic and cavitation characteristics of the vane pump, extending the service life of the vane pump blades 1 and improving the efficiency of the device.

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

[0082] The velocity moments at blade inlet 13 and blade outlet 14, distributed along the axial streamlines, conform to a preset function. The preset function for the velocity moment distribution along the axial streamlines of blade 1 is: C u r=C u1 r 1 +(C u2 r 2 -C u1 r 1 )·F 1 (x)，

[0083] in, C u1 r 1 represents the velocity moment of the axial streamline at the blade inlet end 13. C u2 r 2 represents the velocity moment of the axial streamline at the blade exit end 14. F 1 （x） Let be a dimensionless cubic polynomial function representing the distribution of velocity moments along the axial streamlines in region 1 of the blade. x The ratio between the length of the axial streamline and the blade inlet end 13 at the predetermined position on the axial streamline and the total length of the axial streamline.

[0084] By giving reasonable C u1 r 1. Cu2 r The value of 2, that is, the velocity torque at the blade inlet end 13 and the blade outlet end 14, is the predetermined value of the design. C u1 r 1. C u2 r The value of 2 can be determined based on design experience or by selecting values ​​from the impeller design manual for vane pumps.

[0085] The dimensionless cubic polynomial function representing the distribution of velocity moments along the axial streamlines in region 1 of the blade is:

[0086] F 1 (x)=a 3 ·x 3 +a 2 ·x 2 +a 1 ·x+a 0,

[0087] in, a 3 、a 2 、a 1 、a 0 are all given constants.

[0088] By changing a 3 、a 2 、a 1 、a The given value of 0 and C u1 r 1. C u2 r The predetermined value of 2 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 blade 1.

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

[0090] C u r=C u3 r 3 +(C u4 r 4 -C u3 r 3 )·F 2 (x) ,

[0091] in, C u3r 3 represents the velocity moment of the axial streamline at the guide vane inlet end 43. C u4 r 4 represents the velocity moment of the axial streamline at the guide vane exit end 44. F 2 （x） Let be a dimensionless cubic polynomial function representing the distribution of velocity moments of the axial streamlines at various points in region 4 of the guide vane. x The ratio between the length of the axial streamline and the blade inlet end 13 at the predetermined position on the axial streamline and the total length of the axial streamline.

[0092] By giving reasonable C u3 r 3. C u4 r The value of 4, that is, the velocity torque at the guide vane inlet end 43 and the guide vane outlet end 44, is the predetermined value of the design. C u3 r 3. C u4 r The value of 4 can be determined based on design experience or by selecting values ​​from the impeller design manual for vane pumps.

[0093] The dimensionless cubic polynomial function representing the distribution of velocity moments along the axial streamlines in region 4 of the guide vane is:

[0094] F 2 (x)= b 3 ·x 3 +b 2 ·x 2 +b 1 ·x+b 0,

[0095] in, b 3 、b 2 、b 1 、b 0 are all given constants.

[0096] By changing b 3 、b 2 、b 1 、b The given value of 0 and C u3 r 3. C u4 r The value of 4 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 torque at the blade exit end 14 is equal to the velocity at the guide vane inlet end 43, that is... C u2 r 2= C u3 r 3.

[0098] Furthermore, through design optimization, changes a 3 、a 2 、a 1 、a 0 、b 3 、b 2 、b 1 、b 0 、C u1 r 1 、C u2 r 2 、C u3 r 3 、C u4 r These 12 parameters can alter the variation 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 can be spline interpolation, Lagrange interpolation, Newton interpolation, Hermite interpolation, or piecewise interpolation.

[0100] The following will use more specific embodiments and in conjunction with Figures 1 to 4 The manufacturing methods of the impeller and guide vane 4 of the vane pump are further explained.

[0101] First, based on the actual working conditions of the impeller, determine the velocity torque at the blade inlet end 13 of the axial streamline of the upper crown side 11 of blade 1. C u1 r 1上冠侧 The velocity torque at the blade exit end 14 C u2 r 2上冠侧 The numerical value, and the dimensionless cubic polynomial function of the distribution law of velocity moments of axial streamlines at various points in region 1 of the blade. F 1上冠侧 (x) middle a 3上冠侧 、a 2上冠侧 、a 1上冠侧、a 0上冠侧 The value of the value is used to determine the velocity torque of the blade inlet end 13 of the axial streamline of the lower ring side 12. C u1 r 1下环侧 The velocity torque at the blade exit end 14 C u2 r 2下环侧 The numerical value, and the dimensionless cubic polynomial function of the distribution law of velocity moments of axial streamlines at various points in region 1 of the blade. F 1下环侧 (x) middle a 3下环侧 、a 2下环侧 、a 1下环侧 、a 0下环侧 The value; simultaneously, the velocity torque of the guide vane inlet end 43, which is the axial streamline of the guide vane 4 on the upper annular plate side 41, is determined. C u3 r 3上环板侧 The velocity torque at the guide vane outlet end 44 C u4 r 4上环板侧 The numerical value, and the dimensionless cubic polynomial function F of the distribution law of velocity moments of the axial streamlines in region 4 of the guide vane. 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 value of the guide vane inlet 43 is determined simultaneously, along with the velocity torque of the axial streamline of the lower ring plate side 42. C u3 r 3下环板侧 The velocity torque at the guide vane outlet end 44 C u4 r 4下环板侧 The numerical value, and the dimensionless cubic polynomial function of the distribution law of velocity moments of the axial streamlines in region 4 of the guide vane. F 2下环板侧 (x )middle 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, advantageously, facilitates production. C 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 This determines the velocities of the upper crown side 11 and lower ring side 12 of blade 1, and the velocities of the upper ring plate 5 and lower ring plate 6 of guide vane 4, thus determining the shapes of blade 1 and guide vane 4. It is known that there are countless axial streamlines between the axial streamlines of the upper crown side 11 and the lower ring side 12, and countless more axial streamlines between the axial streamlines of the upper ring plate side 41 and the lower ring plate side 42. These axial streamlines are impossible to exhaustively list. Therefore, interpolation can be used to determine the axial streamlines at other locations, thus determining the shapes of blade 1 and guide vane 4.

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

[0103] According to the manufacturing method of the impeller and guide vane 4 of the present invention, an impeller and guide vane 4 that satisfies a cubic polynomial function can be designed through the above steps. This manufacturing method of the impeller and guide vane 4 is simple to design and easy to implement. Applying this 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 fit between the blade 1 and the guide vane 4 better, and the flow impact smaller, thereby improving the hydraulic and cavitation characteristics of the vane pump, and thus extending the service life and efficiency of the vane pump.

[0104] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

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

Claims

1. A vane pump characterized by, Comprise: Blades, which are arranged between the upper cover plate and the lower cover plate and jointly constitute an impeller with the upper cover plate and the lower cover plate; the blades have 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 blades are blade inlet ends and blade outlet ends respectively; Guide vanes, which are arranged at the blade outlet ends, opposite ends of the guide vanes are guide vane inlet ends and guide vane outlet ends respectively, the guide vane inlet ends are adjacent to the blade outlet ends; the guide vanes are arranged between the upper ring plate and the lower ring plate, the guide vanes have an upper ring plate side connected to the upper ring plate and a lower ring plate side connected to the lower ring plate; the distribution of the velocity moment of the blades and the guide vanes along the axial surface streamline conforms to a preset function; The preset function of the distribution of the velocity moment of the blades along the axial surface streamline is: C u r=C u1 r 1 +(C u2 r 2 -C u1 r 1 )·F 1 (x) ， wherein, C u1 r 1 is the velocity moment of the meridional streamlines at the inlet end of the blade, C u2 r 2 is the velocity moment of the meridional streamlines at the outlet end of the blade, F 1 （x） is a dimensionless cubic polynomial function of the distribution law of the velocity moment of the meridional streamlines throughout the blade area, x corresponding to the ratio between the length of the meridional streamline between a predetermined position on the meridional streamline and the inlet end of the blade and the total length of the meridional streamline. The preset function of the distribution of the velocity moment of the guide vanes along the axial surface streamline is: C u r=C u3 r 3 +(C u4 r 4 -C u3 r 3 )·F 2 (x) ， wherein, C u3 r 3 is the velocity moment of the meridional streamline at the inlet end of the vanes, C u4 r 4 is the velocity moment of the meridional streamline at the outlet end of the vanes, F 2 （x） is a dimensionless cubic polynomial function of the distribution law of the velocity moment of the meridional streamline throughout the vane region, x corresponding to the predetermined position on the meridional streamline and the ratio between the length of the meridional streamline and the total length of the meridional streamline between the inlet end of the vanes. The velocity moment of the blade outlet end is equal to the velocity of the guide vane inlet end.

2. A vane pump according to claim 1, characterized in that The non-dimensional cubic polynomial function of the distribution of the velocity moment of the axial surface streamline at each position in the blade area is: F 1 (x)=a 3 ·x 3 +a 2 ·x 2 +a 1 ·x+a 0， wherein a 3 、a 2 、a 1 、a 0 are all given constants.

3. The vane pump of claim 1, wherein The non-dimensional cubic polynomial function of the distribution of the velocity moment of the axial surface streamline at each position in the guide vane area is: F 2 (x)= b 3 ·x 3 +b 2 ·x 2 +b 1 ·x+b 0， wherein b 3 、b 2 、b 1 、b 0 are given constants.

4. A method of controllably loading a blade and vane combination, characterized by, The blades and the guide vanes are the blades and the guide vanes in the blade pump of any one of claims 1-3 respectively, and the joint manufacturing method comprises: According to the use requirements of the impeller, the velocity moment of the blade inlet end, the velocity moment of the blade outlet end, and the non-dimensional cubic polynomial function of the distribution of the velocity moment of the axial surface streamline at each position in the blade area on at least two axial surface streamlines in the direction from the upper crown side to the lower ring side of the blades are determined to determine the shape of the blades; According to the use requirements of the guide vanes, the velocity moment of the guide vane inlet end, the velocity moment of the guide vane outlet end, and the non-dimensional cubic polynomial function of the distribution of the velocity moment of the axial surface streamline at each position in the guide vane area on at least two axial surface streamlines in the direction from the upper ring plate side to the lower ring plate side of the guide vanes are determined to determine the shape of the guide vanes; According to the at least two axial surface streamlines, the axial surface streamlines at other positions of the impeller and the guide vanes are determined by an interpolation method to obtain blades and guide vanes with a predetermined shape.

5. The controllable load vane and guide vane co- manufacturing method of claim 4, wherein, The distribution of the velocity moment of the blade inlet end and the velocity moment of the blade outlet end along the axial surface streamline conforms to a preset function, the preset function of the distribution of the velocity moment of the blades along the axial surface streamline is: C u r=C u1 r 1 +(C u2 r 2 -C u1 r 1 )·F 1 (x) ， wherein, C u3 r 3 is the velocity moment of the meridional streamline at the inlet end of the vanes, C u4 r 4 is the velocity moment of the meridional streamline at the outlet end of the vanes, F 2 （x） is a dimensionless cubic polynomial function of the distribution law of the velocity moment of the meridional streamline throughout the vane region, x corresponding to the ratio between the length of the meridional streamline between a predetermined position on the meridional streamline and the inlet end of the vane and the total length of the meridional streamline.

6. The controllable load vane and guide vane co- manufacturing method of claim 5, wherein, The non-dimensional cubic polynomial function of the distribution of the velocity moment of the axial surface streamline at each position in the blade area is: F 1 (x)=a 3 ·x 3 +a 2 ·x 2 +a 1 ·x+a 0， wherein, a 3 、a 2 、a 1 、a 0 are all given constants.

7. The controllable load vane and guide vane co- manufacturing method according to any one of claims 4-6, characterized in that, The preset function of the distribution of the velocity moment of the guide vanes along the axial surface streamline is: C u r=C u3 r 3 +(C u4 r 4 -C u3 r 3 )·F 2 (x) ， wherein, C u3 r 3 is the velocity moment of the meridional streamline at the inlet end of the vanes, C u4 r 4 is the velocity moment of the meridional streamline at the outlet end of the vanes, F 2 （x） is a dimensionless cubic polynomial function of the distribution law of the velocity moment of the meridional streamline throughout the vane region, x corresponds to the ratio between the length of the meridional streamline between a predetermined position on the meridional streamline and the inlet end of the vane and the total length of the meridional streamline.

8. The controllable load vane and bucket combination method of claim 7, wherein, The non-dimensional cubic polynomial function of the distribution of the velocity moment of the axial surface streamline at each position in the guide vane area is: F 2 (x)= b 3 ·x 3 +b 2 ·x 2 +b 1 ·x+b 0， wherein b 3 、b 2 、b 1 、b 0 are given constants.

9. The controllable load vane and bucket combination method of claim 4, wherein, The at least two axial surface streamlines include the axial surface streamlines at the upper crown side and the lower ring side in the blade area.

10. The controllable load vane and bucket combination method of claim 4, wherein, The at least two axial surface streamlines include the axial surface streamlines at the upper ring plate side and the lower ring plate side in the guide vane area.

11. The method of claim 4-6, wherein, 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. 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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