Vane pump blades, vane pumps and their usage

Abstract

The present invention discloses a vane of a vane pump, a vane pump and a method for using the vane pump. The vane top of the vane is provided with a groove, the groove is close to the leading edge of the vane, the groove forms openings on the pressure side of the vane and the suction side of the vane, and the opening depth of the groove on the pressure side of the vane is less than the opening depth of the groove on the suction side of the vane. The present invention can significantly inhibit gap leakage vortex and leakage vortex cavitation, which is beneficial to improving the safe and stable operation level and hydraulic efficiency of the vane pump.

Description

Technical Field

[0001] The present invention relates to the technical field of vane pumps, and in particular to a vane of a vane pump, a vane pump and a use method thereof. Background Art

[0002] As a fluid machinery, vane pumps are widely used in various fields such as water conservancy projects and petrochemicals. Improving the operating efficiency of vane pumps is of great significance for energy conservation and emission reduction.

[0003] In a vane pump, due to the inevitable gap between the blades and the inner wall of the impeller chamber, high-pressure fluid will jet from the pressure side through the gap to the suction side, and after interacting with the mainstream, a complex blade tip gap vortex structure will be formed, resulting in flow loss, affecting the efficient operation of the pump, and further inducing blade tip gap leakage vortex cavitation, seriously endangering the stable operation of the pump. 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 blade that can significantly inhibit gap leakage vortex and leakage vortex cavitation, thereby improving the safe and stable operation level and hydraulic efficiency of the vane pump.

[0005] According to the blade of the vane pump of the first aspect of the present invention, a groove is provided on the top of the blade, the groove is close to the leading edge of the blade, the groove forms openings on the pressure side of the blade and the suction side of the blade, and the opening depth of the groove on the pressure side of the blade is less than the opening depth of the groove on the suction side of the blade.

[0006] The blade of the vane pump according to the embodiment of the present invention has the following advantages: first, by opening a groove on the blade top, the groove is close to the leading edge of the blade, and the groove forms an opening on the pressure side and the suction side of the blade, so that a jet can be formed in the groove, and the jet can have an impact on the gap leakage vortex, thereby achieving the effect of suppressing the tip gap leakage vortex; second, by making the opening depth of the groove on the pressure side of the blade smaller than the opening depth of the groove on the suction side of the blade, that is, the groove is a variable depth groove, and the variable depth groove can significantly increase the flow field pressure near the opening of the groove on the suction side of the blade, thereby achieving the effect of suppressing leakage vortex cavitation; third, the groove size of the embodiment of the present invention is small, and the groove has little effect on the energy characteristics of the overall structure of the blade, and is suitable for any vane pump with a gap between the blade top and the inner wall of the runner chamber. From the above, the present invention can effectively suppress the generation of tip gap leakage vortex and leakage vortex cavitation of the blade in the vane pump, which is conducive to improving the safe and stable operation level of the vane pump and the hydraulic efficiency of the vane pump, while having little effect on the energy characteristics of the vane pump.

[0007] According to some embodiments of the invention, the depth of the groove increases linearly along a direction from the pressure side of the blade to the suction side of the blade.

[0008] According to some embodiments of the present invention, an arrangement direction of the openings of the grooves on the pressure side and the suction side forms a set angle with a blade tip chord line of the blade.

[0009] According to some embodiments of the present invention, an arrangement direction of the openings of the grooves on the pressure side and the suction side is perpendicular to a blade tip chord line of the blade.

[0010] According to some embodiments of the present invention, the opening edge of the groove at the blade top includes a first edge and a second edge, the first edge is located between the leading edge of the blade and the second edge, the spacing between the first edge and the leading edge of the blade is c, the distance between the starting point of the clearance leakage vortex of the blade and the leading edge of the blade is c0, the chord length of the blade top is C, and c0<c≤0.3C.

[0011] According to some embodiments of the present invention, two opposite side walls of the groove along a blade tip chord direction of the blade are parallel to each other.

[0012] The second aspect of the present invention also provides a vane pump.

[0013] A vane pump according to an embodiment of the second aspect of the present invention comprises a runner chamber and a vane of the vane pump according to any one embodiment of the first aspect of the present invention, wherein the vane is rotatably disposed in the runner chamber.

[0014] Since the vane pump according to the embodiment of the present invention includes the vane of the vane pump according to the embodiment of the first aspect of the present invention, the vane pump according to the embodiment of the present invention has at least the following advantages: first, by providing a groove at the top of the blade, the groove is close to the leading edge of the blade, and the groove forms an opening on the pressure side and the suction side of the blade, so that a jet can be formed in the groove, and the jet can have an impact on the gap leakage vortex, thereby achieving the effect of suppressing the tip gap leakage vortex; second, by making the opening depth of the groove on the pressure side of the blade less than the opening depth of the groove on the suction side of the blade, that is, the groove is a variable depth groove, and the variable depth groove can significantly increase the flow field pressure near the opening of the groove on the suction side of the blade, thereby achieving the effect of suppressing leakage vortex cavitation; third, the groove size of the embodiment of the present invention is small, and the groove has little effect on the energy characteristics of the overall structure of the blade, and is suitable for vane pumps with a gap between the blade top and the inner wall surface of the runner chamber of any blade. From the above, the present invention can effectively suppress the generation of tip gap leakage vortex and leakage vortex cavitation of the blades in the vane pump, which is conducive to improving the safe and stable operation level of the vane pump and the hydraulic efficiency of the vane pump, while having little effect on the energy characteristics of the vane pump.

[0015] According to some embodiments of the present invention, the depth of the groove is not greater than the distance between the tip of the blade and the inner wall surface of the runner chamber.

[0016] According to some embodiments of the present invention, the distance between two opposite side walls of the groove along the blade tip chord direction of the blade is w, the distance between the blade tip and the inner wall surface of the runner chamber is τ, and 0.5τ<w≤2τ.

[0017] The third aspect of the present invention further provides a method for using the vane pump.

[0018] A method for using a vane pump according to an embodiment of the third aspect of the present invention is based on a vane pump according to any one embodiment of the second aspect of the present invention, comprising: replacing the vanes of different specifications according to different operating conditions of the vane pump, the grooves of the vanes of different specifications having different structures.

[0019] According to the method of using the vane pump in an embodiment of the present invention, by replacing blades of different specifications according to different operating conditions of the vane pump, the groove can achieve better or best suppression effect on gap leakage vortex and leakage vortex cavitation under different operating conditions of the vane pump.

[0020] 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

[0021] 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:

[0022] Figure 1 It is a schematic structural diagram of the vanes of the vane pump according to an embodiment of the present invention.

[0023] Figure 2 This is a partial enlarged view of the vanes of the vane pump according to an embodiment of the present invention.

[0024] Figure 3 It is a schematic diagram of a blade in the related art and a gap leakage vortex generated by the blade in the impeller flow channel.

[0025] Figure 4 Schematic diagram of a blade in an embodiment of the present invention and a gap leakage vortex generated by the blade in an impeller flow channel.

[0026] Figure 5 It is a schematic diagram of a blade in the related art and leakage vortex cavitation generated by the blade in the impeller flow channel.

[0027] Figure 6Schematic diagram of a blade in an embodiment of the present invention and a leakage vortex cavitation structure generated by the blade in an impeller flow channel.

[0028] Reference numerals:

[0029] Vane 100 of a vane pump;

[0030] Blade tip 10; groove 20; first edge 201; second edge 202; leading edge 30;

[0031] Pressure side 40; suction side 50; blade tip chord line 60; starting point of gap leakage vortex 70; trailing edge 80;

[0032] Leaf root 90;

[0033] Gap leakage vortex A; leakage vortex cavitation B. DETAILED DESCRIPTION

[0034] In order to make the purpose, technical solution and advantages of the embodiments of the present invention clearer, the technical solution in the embodiments of the present invention will be clearly described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0035] Unless otherwise defined, all technical and scientific terms used in the present invention have the same meanings as those commonly understood by technicians in the technical field of the present invention; the terms used in the present invention and the specification of the invention are only for the purpose of describing specific embodiments and are not intended to limit the present invention; the terms "including" and "having" and any variations thereof in the specification and claims of the present invention and the above-mentioned drawings are intended to cover non-exclusive inclusions. The terms "first", "second", etc. in the specification and claims of the present invention or the above-mentioned drawings are used to distinguish different objects, rather than to describe a specific order or a primary and secondary relationship.

[0036] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", and "attached" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be the internal communication of two elements. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0037] The term "and / or" in the present invention is only a description of the association relationship of the associated objects, indicating that there can be three relationships. For example, A and / or B can represent: A exists alone, A and B exist at the same time, and B exists alone. In addition, the character " / " in the present invention generally indicates that the associated objects before and after are in an "or" relationship.

[0038] In the embodiments of the present invention, the same reference numerals represent the same components, and for the sake of brevity, detailed descriptions of the same components are omitted in different embodiments. It should be understood that the thickness, length, width and other dimensions of various components in the embodiments of the present invention shown in the drawings, as well as the overall thickness, length, width and other dimensions of the integrated device are only exemplary and should not constitute any limitation to the present invention.

[0039] The term "plurality" used in the present invention refers to two or more (including two).

[0040] 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, 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, or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0041] Combine the following Figures 1 to 6 The vane 100 of the vane pump, the vane pump and the method of using the vane pump of the present invention are described.

[0042] like Figures 1 to 6 As shown, according to the blade 100 of the vane pump according to the first embodiment of the present invention, the blade top 10 of the blade 100 is provided with a groove 20, the groove 20 is close to the leading edge 30 of the blade 100, the groove 20 forms openings on the pressure side 40 of the blade 100 and the suction side 50 of the blade 100, and the opening depth of the groove 20 on the pressure side 40 of the blade 100 is less than the opening depth of the groove 20 on the suction side 50 of the blade 100.

[0043] More specifically, the blade root 90 of the blade 100 refers to the connecting portion of the blade 100 that fixes the blade 100 on the drum of the vane pump, and the blade tip 10 of the blade 100 is the side of the blade 100 facing away from the blade root 90 .

[0044] When the vane pump is working, the pressure side 40 of the blade 100 does work on the fluid and has a squeezing effect on the fluid; at the same time, due to the rotation of the blade 100, the fluid tends to separate from the wall on the suction side 50 of the blade 100, resulting in a decrease in pressure on the suction side 50, which is manifested as the suction side 50 of the blade 100 having a suction effect on the fluid.

[0045] The blade profile of blade 100 is a blade cross-section having an aerodynamic shape. The leading edge 30 of blade 100 refers to the portion of the blade profile of blade 100 at the front end in the rotation direction connecting the pressure side 40 and the suction side 50. The trailing edge 80 of blade 100 refers to the portion of the blade profile of blade 100 at the rear end in the rotation direction connecting the pressure side 40 and the suction side 50.

[0046] The clearance leakage vortex A of the blade 100 is close to the leading edge 30 of the blade 100 , so the groove 20 needs to be arranged close to the leading edge 30 of the blade 100 .

[0047] A groove 20 is opened at the blade top 10 of the blade 100, and the groove 20 forms openings on the pressure side 40 of the blade 100 and the suction side 50 of the blade 100, so that the groove 20 can utilize the pressure difference between the pressure side 40 of the blade 100 and the suction side 50 of the blade 100 to form a jet in the groove 20, and the jet can have an impact on the gap leakage vortex A, thereby inhibiting the further development of the gap leakage vortex A.

[0048] The opening depth of the groove 20 on the pressure side 40 of the blade 100 is less than the opening depth of the groove 20 on the suction side 50 of the blade 100. Since the opening depth of the groove 20 on the suction side 50 of the blade 100 is larger, the fluid flow rate is slower, that is, the pressure at the opening of the groove 20 on the suction side 50 of the present invention increases, and thus the flow field pressure near the opening of the groove 20 on the suction side 50 of the blade 100 can be significantly increased, so that the leakage vortex cavitation B can be effectively suppressed.

[0049] You can refer to Figure 3 and Figure 4 ,in, Figure 3 Schematic diagram of a blade in the related art and a gap leakage vortex A generated by the blade in the impeller flow channel, Figure 4 Schematic diagram of the blade in the embodiment of the present invention and the gap leakage vortex A generated by the blade 100 in the impeller flow channel. By comparison, it can be seen that after the groove 20 is set on the blade 100, the size of the gap leakage vortex A is significantly reduced, proving that the setting of the groove 20 in the embodiment of the present invention can significantly suppress the gap leakage vortex A.

[0050] You can refer to Figure 5 and Figure 6 As shown, Figure 5 As shown, Figure 5Schematic diagram of a blade in the related art and leakage vortex cavitation B generated by the blade 100 in the impeller flow channel, Figure 6 Schematic diagram of the blade 100 and the leakage vortex cavitation B structure generated by the blade 100 in the impeller flow channel in the embodiment of the present invention. By comparison, it can be seen that the size of the leakage vortex cavitation B is significantly reduced in the blade 100 provided with the groove 20 in the embodiment of the present invention, proving that the groove 20 in the embodiment of the present invention can significantly suppress the leakage vortex cavitation B.

[0051] The blade 100 of the vane pump according to the embodiment of the present invention has the following advantages: first, by opening a groove 20 on the blade tip 10 of the blade 100, the groove 20 is close to the leading edge 30 of the blade 100, and the groove 20 forms openings on the pressure side 40 of the blade 100 and the suction side 50 of the blade 100, a jet can be formed in the groove 20, and the jet can have an impact on the gap leakage vortex A, thereby achieving the effect of suppressing the gap leakage vortex A of the blade tip 10; second, by making the opening depth of the groove 20 on the pressure side 40 of the blade 100 less than the opening depth of the groove 20 on the suction side 50 of the blade 100, that is, the groove 20 is a variable depth groove, and the variable depth groove can significantly increase the flow field pressure near the opening of the groove 20 on the suction side 50 of the blade 100, thereby achieving the effect of suppressing leakage vortex cavitation B; third, the groove 20 of the embodiment of the present invention is small in size, and the groove 20 has little effect on the energy characteristics of the overall structure of the blade 100, and is suitable for vane pumps with a gap between the blade tip of any blade and the inner wall surface of the runner chamber. As described above, the present invention can effectively suppress the generation of leakage vortex A and leakage vortex cavitation B in the gap between the blade tip 10 of the blade 100 in the vane pump, which is beneficial to improving the safe and stable operation level of the vane pump and the hydraulic efficiency of the vane pump, while having little impact on the energy characteristics of the vane pump.

[0052] According to some embodiments of the present invention, Figure 1 and Figure 2 As shown, the depth of the groove 20 increases linearly along the direction from the pressure side 40 of the blade 100 to the suction side 50 of the blade 100, thereby forming a variable depth groove 20, which can significantly increase the flow field pressure near the opening of the groove 20 on the suction side 50 of the blade 100, thereby effectively suppressing leakage vortex cavitation B. The depth of the groove 20 increases linearly, so that the processing difficulty is low. In some embodiments, the depth of the groove 20 may also increase nonlinearly along the direction from the pressure side 40 of the blade 100 to the suction side 50 of the blade 100.

[0053] like Figure 2As shown, the opening edge of the groove 20 at the blade tip 10 includes a first edge 201 and a second edge 202. The first edge 201 is located between the leading edge 30 of the blade 100 and the second edge 202. A coordinate system is established with the vertex of the first edge 201 close to the pressure side 40 of the blade 100 as the origin of the coordinate system. The straight line where the first edge 201 is located is the t-axis. The direction from the end point of the first edge 201 close to the pressure side 40 of the blade 100 to the end point of the first edge 201 close to the suction side 50 is the positive direction of the t-axis. The direction along the depth direction of the groove 20 and away from the blade 100 is the positive direction of the h-axis. In this coordinate system, the depth control equation of the groove 20 is:

[0054]

[0055] Among them, h p is the opening depth of the groove 20 on the pressure side 40 of the blade 100, h s is the opening depth of the groove 20 at the suction side 50 of the blade 100, l g is the size of the first edge 201 of the groove 20. When the distance between the first edge 201 and the leading edge 30 of the blade 100 is determined, l g The only certainty.

[0056] According to some embodiments of the present invention, the arrangement direction of the openings of the grooves 20 on the pressure side 40 and the suction side 50 forms a set angle with the tip chord line 60 of the blade 100. It should be noted that the mid-camber line of the blade profile of the tip 10 of the blade 100 intersects with the leading edge 30 and the trailing edge 80 of the blade profile of the tip 10 of the blade 100 at two points respectively, and the line between the two points is the tip chord line 60 of the blade 100. The size of the set angle in the embodiments of the present invention can be 90°, 89°, 88°, 85°, 80°, 91°, 92°, 93°, 95°, 100° or any value between any two of them, etc.

[0057] According to some embodiments of the present invention, the arrangement direction of the openings of the groove 20 on the pressure side 40 and the suction side 50 is perpendicular to the blade tip chord line 60 of the blade 100. In this way, it is easy to process, the processing difficulty is lower, the jet intensity in the groove 20 is high, and the suppression effect of the gap leakage vortex A is good.

[0058] According to some embodiments of the present invention, Figure 1 and Figure 2As shown, the opening edge of the groove 20 at the blade tip 10 includes a first edge 201 and a second edge 202, the first edge 201 is located between the leading edge 30 of the blade 100 and the second edge 202, the spacing between the first edge 201 and the leading edge 30 of the blade 100 is c, the distance between the starting point 70 of the gap leakage vortex of the blade 100 and the leading edge 30 of the blade 100 is c0, the chord length of the blade tip 10 of the blade 100 is C, c0<c≤0.3C. It should be noted that the mid-camber line of the blade profile of the blade tip 10 of the blade 100 intersects with the leading edge 30 and the trailing edge 80 of the blade profile of the blade tip 10 of the blade 100 at two points respectively, the line between the two points is called the blade tip chord line 60 of the blade 100, and the length of the blade tip chord line 60 of the blade 100 is called the chord length.

[0059] It should be noted that the distance between the starting point 70 of the gap leakage vortex of the blade 100 and the leading edge 30 of the blade 100 can be determined by experiments or numerical simulation results. The groove 20 can only suppress the gap leakage vortex A when it is located on the downstream side of the starting point 70 of the gap leakage vortex, so c should be greater than c0. In order to achieve a better suppression effect on the formation of the gap leakage vortex A, the gap leakage vortex A should be suppressed at the early stage of its formation, and c should be less than or equal to 0.3C.

[0060] According to some embodiments of the present invention, the two opposite side walls of the groove 20 along the direction of the blade tip chord line 60 of the blade 100 are parallel to each other. In this way, processing is convenient, and as the incoming flow parameters change, the groove 20 can always play a role in suppressing the gap leakage vortex A and leakage vortex cavitation B. In some embodiments, the two opposite side walls of the groove 20 along the direction of the blade tip chord line 60 of the blade 100 may also be non-parallel. For example, the spacing between the two opposite side walls along the direction of the blade tip chord line 60 of the blade 100 near the suction side 50 is greater than the spacing between the pressure side 40, which can also play a role in suppressing the gap leakage vortex A and leakage vortex cavitation B under certain working conditions of the vane pump.

[0061] The second aspect of the present invention also provides a vane pump.

[0062] The vane pump according to the second embodiment of the present invention comprises a circulation chamber and a vane 100 of the vane pump according to any one embodiment of the first embodiment of the present invention, wherein the vane 100 is rotatably arranged in the circulation chamber. It is understood that the vane pump comprises a pump housing, and the pump housing defines the circulation chamber.

[0063] Since the vane pump of the present invention includes the vane 100 of the vane pump according to any one embodiment of the first aspect of the present invention, the vane pump of the present invention has at least the following advantages: first, by providing a groove 20 at the blade tip 10 of the vane 100, the groove 20 is close to the leading edge 30 of the vane 100, and the groove 20 forms an opening at the pressure side 40 of the vane 100 and the suction side 50 of the vane 100, so that a jet can be formed in the groove 20, and the jet can have an impact on the gap leakage vortex A, thereby achieving the effect of suppressing the gap leakage vortex A at the blade tip 10; second, By making the opening depth of the groove 20 on the pressure side 40 of the blade 100 smaller than the opening depth of the groove 20 on the suction side 50 of the blade 100, that is, the groove 20 is a variable depth groove 20, the variable depth groove 20 can significantly increase the flow field pressure near the opening of the groove 20 on the suction side 50 of the blade 100, thereby achieving the effect of suppressing leakage vortex cavitation B; thirdly, the size of the groove 20 in the embodiment of the present invention is small, and the groove 20 has little effect on the energy characteristics of the overall structure of the blade 100, and is suitable for any vane pump with a gap between the blade tip and the inner wall of the runner chamber. From the above, the present invention can effectively suppress the generation of leakage vortex A and leakage vortex cavitation B in the gap between the blade tip 10 of the blade 100 in the vane pump, which is beneficial to improving the safe and stable operation level of the vane pump and the hydraulic efficiency of the vane pump, while having little effect on the energy characteristics of the vane pump.

[0064] According to some embodiments of the present invention, the depth of the groove 20 is not greater than the distance between the tip 10 of the blade 100 and the inner wall surface of the runner chamber. In this way, the flow loss of the vane pump will not be too large. More specifically, for example, the ratio of the depth of the groove 20 to the distance between the tip 10 of the blade 100 and the inner wall surface of the runner chamber is 0.9, 0.8, 0.7, 0.6, etc. or any value between two of the values. The depth of the groove 20 is not greater than the distance between the tip 10 of the blade 100 and the inner wall surface of the runner chamber, including that the opening depth of the groove 20 on the pressure side 40 of the blade 100 and the opening depth of the groove 20 on the suction side 50 of the blade 100 are both not greater than the distance between the tip 10 of the blade 100 and the inner wall surface of the runner chamber.

[0065] According to some embodiments of the present invention, Figure 2 As shown, the distance between the two opposite side walls of the groove 20 along the tip chord line 60 of the blade 100 is w, that is, the width of the groove 20 is w, and the distance between the tip 10 of the blade 100 and the inner wall of the runner chamber is τ, 0.5τ<w≤2τ.

[0066] More specifically, for example, the distance between two opposite side walls of the groove 20 along the blade top chord line 60 of the blade 100 is 0.6τ, 0.7τ, 0.8τ, 0.9τ, 1τ, 1.1τ, 1.3τ, 1.5τ, 1.7τ, 1.9τ, 2τ, etc. or any value between any two of them.

[0067] It should be noted that w>0.5τ, so that the width of the groove 20 is not too small, so that a jet with sufficient strength can be formed in the groove 20. At the same time, w≤2τ, so that the width of the groove 20 is not too large. An excessively large width of the groove 20 will cause significant damage to the structure of the blade 100 and increase the flow loss, which will lead to a decrease in the energy characteristics of the vane pump.

[0068] It should be noted that obtaining Figures 3 to 6 The simulation results shown correspond to the following simulation parameters: the chord length of the blade tip 10 of the blade 100 C = 100 mm, the span of the blade 100 (i.e., the length from the blade tip to the blade root) S = 148 mm, the maximum thickness of the blade 100 (the maximum dimension perpendicular to the span direction and the chord direction) T = 9.9 mm, the distance between the blade tip 10 of the blade 100 and the inner wall surface of the runner chamber is 2 mm, and the incoming flow velocity v = 10 m / s. The arrangement direction of the openings of the groove 20 on the pressure side 40 of the blade 100 and the suction side 50 of the blade 100 is perpendicular to the chord line of the blade tip 10 of the blade 100, the distance between the two opposite side walls of the groove 20 along the chord line direction of the blade tip 100 is w = 2 mm, and the opening depth h of the groove 20 on the pressure side 40 of the blade 100 is 1. p =1 mm, the opening depth h of the groove 20 on the suction side 50 of the blade 100 s =2mm, the top opening edge of the groove 20 at the blade top 10 includes a first edge 201 and a second edge 202, the first edge 201 is located between the leading edge 30 of the blade 100 and the second edge 202, and the spacing between the first edge 201 and the leading edge 30 of the blade 100 is c=15mm.

[0069] The third aspect of the present invention further provides a method for using the vane pump.

[0070] The method for using a vane pump according to an embodiment of the third aspect of the present invention is based on the vane pump according to any embodiment of the second aspect of the present invention, and includes: replacing vanes 100 of different specifications according to different operating conditions of the vane pump, and the structures of the grooves 20 of the vanes 100 of different specifications are different. Here, the different structures of the grooves 20 of the vanes 100 of different specifications include different opening depths of the grooves 20 on the pressure side 40 of the vane 100, different opening depths of the grooves 20 on the suction side 50 of the vane 100, different arrangement directions of the openings of the grooves 20 on the pressure side 40 and the suction side 50 and the blade top chord line 60 of the blade 100, different set angles, different spacings between the first edge 201 of the groove 20 and the leading edge 30 of the blade 100, and different distances between the two opposite side walls of the groove 20 along the direction of the blade top chord line 60 of the blade 100.

[0071] More specifically, for example, according to the actual use condition of the vane pump, the vane pump having the vanes 100 of corresponding specifications is directly replaced.

[0072] It should be noted that when the operating conditions of the vane pump change, the incoming flow parameters and the blade tip clearance flow intensity will change, and correspondingly, the inhibitory effect of the groove 20 on the gap leakage vortex A and the leakage vortex cavitation B will also change. According to the method for using the vane pump of an embodiment of the present invention, by replacing blades 100 of different specifications according to different operating conditions of the vane pump, the groove 20 can achieve better or best inhibitory effect on the gap leakage vortex A and the leakage vortex cavitation B under different operating conditions of the vane pump.

[0073] 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 having a variable depth groove, characterized in that: The blade tip (10) of the blade (100) is provided with a groove (20), the groove (20) is close to the leading edge (30) of the blade (100), the groove (20) forms openings at the pressure side (40) of the blade (100) and the suction side (50) of the blade (100), and the opening depth of the groove (20) at the pressure side (40) of the blade (100) is smaller than the opening depth of the groove (20) at the suction side (50) of the blade (100); Two opposite side walls of the groove (20) along the direction of the blade tip chord line (60) of the blade (100) are parallel to each other.

2. The vane of a vane pump having a variable depth groove according to claim 1, characterized in that: The depth of the groove (20) increases linearly along the direction from the pressure side (40) of the blade (100) to the suction side (50) of the blade (100).

3. The vane of a vane pump having a variable depth groove according to claim 1, characterized in that: The arrangement direction of the openings of the grooves (20) on the pressure side (40) and the suction side (50) forms a set angle with the tip chord line (60) of the blade (100).

4. The vane of a vane pump having a variable depth groove according to claim 3, characterized in that: The arrangement direction of the openings of the groove (20) on the pressure side (40) and the suction side (50) is perpendicular to the tip chord line (60) of the blade (100).

5. The vane of a vane pump having a variable depth groove according to claim 1, characterized in that: The opening edge of the groove (20) at the blade tip (10) comprises a first edge (201) and a second edge (202), the first edge (201) being located between the leading edge (30) of the blade (100) and the second edge (202), and the distance between the first edge (201) and the leading edge (30) of the blade (100) being c The distance between the starting point (70) of the gap leakage vortex of the blade (100) and the leading edge (30) of the blade (100) is c 0, the chord length of the blade tip (10) of the blade (100) is C , c 0 <c≤0.3C .

6. A vane pump, characterized in that: It comprises a runner chamber and a blade (100) according to any one of claims 1 to 5, wherein the blade (100) is rotatably arranged in the runner chamber.

7. The vane pump according to claim 6, characterized in that: The depth of the groove (20) is no greater than the distance between the blade tip (10) of the blade (100) and the inner wall surface of the runner chamber.

8. The vane pump according to claim 6 or 7, characterized in that: The distance between two opposite side walls of the groove (20) in the direction of the blade tip chord line (60) of the blade (100) is w The distance between the tip (10) of the blade (100) and the inner wall surface of the runner chamber is τ, 0.5 τ < w ≤2 τ .

9. A method for using a vane pump, characterized in that: Based on the vane pump according to any one of claims 6 to 8, the method comprises: replacing the vanes (100) of different specifications according to different operating conditions of the vane pump, and the structures of the grooves (20) of the vanes (100) of different specifications are different.

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