CN111677689A - Design method of vibration and noise reduction mixed flow pump or axial flow pump - Google Patents
Design method of vibration and noise reduction mixed flow pump or axial flow pump Download PDFInfo
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- CN111677689A CN111677689A CN202010577429.2A CN202010577429A CN111677689A CN 111677689 A CN111677689 A CN 111677689A CN 202010577429 A CN202010577429 A CN 202010577429A CN 111677689 A CN111677689 A CN 111677689A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/181—Axial flow rotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps
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- General Engineering & Computer Science (AREA)
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Abstract
The invention discloses a design method of a vibration and noise reduction mixed flow pump or axial flow pump, and relates to the technical field of hydropower equipment. The design method of the invention is that the vane profile on each flow surface of the vane from the hub to the rim of the mixing/axial-flow pump rotates the same angle in the same direction in the circumferential direction relative to the previous vane profile, the rotation angle of the vane profile on the flow surface of the vane at the rim relative to the vane profile on the flow surface of the vane at the hub is 25-50 degrees; the number of the blades of the mixed flow pump is increased, and the increased number is 50% -100% of the number of the blades of the same type of conventional mixed/axial flow pump. The invention provides a novel blade shape design, which can (but is not limited to) rotate blade profiles on each flow surface from a hub to a rim by a certain angle relative to the previous blade profile in the circumferential direction on the basis of the blade obtained by the traditional design method. The hydraulic vibration of the pump is obviously low, the vibration reduction effect of the product is obvious, and the noise is low.
Description
Technical Field
The invention relates to the technical field of hydroelectric power generation equipment, in particular to a design method of a vibration and noise reduction mixed flow pump or axial flow pump.
Background
The hydraulic design task of the mixing/axial-flow pump is to determine main structural parameters of an impeller, a water suction chamber, a water pressing chamber and other flow passage components, wherein the determination of the hydraulic parameters of blades and guide vanes of the impeller has great influence on the hydraulic efficiency, the cavitation resistance, the noise control of a pump station and the like of the pump. In the design of mixed flow pump and axial flow pump, in order to make the radial component of the acting force of the blade on the water flow smaller and satisfy the assumption that the flow state is close to the independence of the flow surface, the inlet and outlet edges of the blade are always close to the vertical direction of the water flow. It is always endeavored to arrange the blade inlet/outlet edges in one axial plane. Even if the blade wrap angles differ in the flow surfaces from the hub to the rim, it is not possible to arrange the inlet and outlet edges in one axial plane each. Designers also always consider the inlet and outlet sides together so that they are each as close as possible to being in one axial plane. When hydraulic design is carried out by the processing mode, each flow surface can be calculated respectively, the design difficulty is reduced, and good hydraulic performance is easy to obtain. Meanwhile, the blade has better manufacturability, and is convenient to process additionally. However, the blade thus obtained has a poor vibration damping effect. The product with higher requirement on noise cannot be met.
Disclosure of Invention
The invention aims to solve the problems that the design vibration reduction effect of mixed flow pump blades is poor and the product with higher noise requirement cannot be met in the prior art. The invention provides a novel blade shape design, which can (but is not limited to) rotate blade profiles on each flow surface from a hub to a rim by a certain angle relative to the previous blade profile in the circumferential direction on the basis of the blade obtained by the traditional design method. The hydraulic vibration of the pump is obviously low, the vibration reduction effect of the product is obvious, and the noise is low.
In order to solve the problems in the prior art, the invention is realized by the following technical scheme:
a design method of a mixed flow pump for vibration and noise reduction is characterized in that: the method comprises the following steps:
rotating the blade profile of each flow surface of the blade from the hub to the rim of the mixed flow pump in the same direction by the same angle delta phi relative to the previous blade profile in the circumferential direction, wherein the rotating angle phi of the blade profile of the flow surface of the blade at the rim relative to the blade profile of the flow surface of the blade at the hub is 25-50 degrees;
increasing the number of blades of the mixed flow pump, wherein the increased number is 50-100% of the number of blades of the same type of conventional mixed flow pump;
the blades are impeller blades and/or guide vane blades.
The vane profile on each flow surface of the impeller blade from the hub to the rim is sequentially rotated in the circumferential direction relative to the previous vane profile in the opposite direction to the vane profile on each flow surface of the guide vane blade from the hub to the rim.
The impeller blades are arranged in a backswept mode, specifically, the blade profile at the wheel edge rotates backwards by an angle relative to the blade profile at the wheel hub, and the backward rotation specifically refers to a direction opposite to the rotation direction of the impeller.
The guide vane blades are arranged in a forward tilting mode, the forward tilting mode specifically means that the blade profile at the wheel edge rotates forwards by an angle relative to the blade profile at the wheel hub, and the forward rotation specifically means the direction the same as the rotation direction of the impeller.
The invention also provides a design method of the vibration and noise reduction axial flow pump, and solves the problems that the design vibration reduction effect of the axial flow pump blade is poor and the product with higher noise requirement cannot be met in the prior art. The invention provides a novel blade shape design, which can (but is not limited to) rotate blade profiles on each flow surface from a hub to a rim by a certain angle relative to the previous blade profile in the circumferential direction on the basis of the blade obtained by the traditional design method. The hydraulic vibration of the pump is obviously low, the vibration reduction effect of the product is obvious, and the noise is low.
A design method of an axial flow pump for vibration and noise reduction is characterized in that: the method comprises the following steps:
rotating the blade profile of each flow surface of the blades of the axial flow pump from the hub to the rim by the same angle delta phi in the same direction in the circumferential direction relative to the previous blade profile, wherein the rotating angle phi of the blade profile on the flow surface of the blades at the rim relative to the blade profile on the flow surface of the blades at the hub is 25-50 degrees;
increasing the number of blades of the axial flow pump, wherein the increased number is 50% -100% of the number of blades of the same type of conventional axial flow pump;
the blades are impeller blades and/or guide vane blades.
The vane profile on each flow surface of the impeller blade from the hub to the rim is sequentially rotated in the circumferential direction relative to the previous vane profile in the opposite direction to the vane profile on each flow surface of the guide vane blade from the hub to the rim.
The impeller blades are arranged in a backswept mode, specifically, the blade profile at the wheel edge rotates backwards by an angle relative to the blade profile at the wheel hub, and the backward rotation specifically refers to a direction opposite to the rotation direction of the impeller.
The guide vane blades are arranged in a forward tilting mode, the forward tilting mode specifically means that the blade profile at the wheel edge rotates forwards by an angle relative to the blade profile at the wheel hub, and the forward rotation specifically means the direction the same as the rotation direction of the impeller.
Compared with the prior art, the beneficial technical effects brought by the invention are as follows:
1. in the prior art, the shape of the cylindrical blade from the back shroud (hub) to the front shroud (rim) is identical, and the whole blade can be a cylindrical surface, i.e. a twisted blade. In both mixed and axial flow pumps, the blades must be twisted because the blade angle must be different on different streamlines from the hub to the rim. The blade proposed by the patent is based on the traditional twisted blade, and is processed again, the relative position of the blade profile on different flow surfaces from the hub to the rim in the circumferential direction is changed, and the angles of the blade profiles, such as the blade placement angle and the liquid flow angle, are not related. After the relative position of the blade profile in the circumferential direction on different flow surfaces from the hub to the rim is changed, the flow conditions are changed, the mutual influence degree among the flow surfaces is redistributed, the water conservancy vibration of the pump is obviously reduced, the vibration reduction effect of the product is obvious, and the noise is low.
2. In the application, the blade profile on each flow surface of the impeller blade or the guide vane blade from the hub to the rim sequentially rotates at a certain angle relative to the previous blade profile in the circumferential direction, and the optimal value of the blade or the guide vane blade for different design objects can be determined only by performing complex calculation, such as CFD analysis, and comprehensively considering indexes such as efficiency, cavitation, vibration, strength and the like and the limitation of materials and process conditions. In a trend, the larger the angle of sweep back or rake forward, the better the damping effect, but the performance in terms of efficiency, cavitation, etc. is adversely affected, and this effect increases with increasing sweep back or rake angle. This effect is not significant when the sweep angle is not too large, but increases with increasing angle. Meanwhile, the larger the angle is, the greater the processing difficulty is, and the strength and rigidity of the blade are weakened. Therefore, for different engineering projects, due to different requirements on efficiency and cavitation indexes and different adopted processing technologies and equipment, the limitation on the sweepback angle is different. In most cases, the optimum sweep angle is approximately 25 to 50 degrees. And the higher the specific speed of the pump, the greater the optimum sweep angle.
3. The number of blades, as well as the sweep angle, is limited by efficiency, cavitation, intensity and process conditions, which need to be determined for the specific subject's specifications. In conventional designs, the number of vanes is determined based on the specific speed of the pump. In most cases, the blade ratio is increased by 50% to 100% from the conventional value for vibration damping. In hydraulic design, the density of the blade cascade has an optimal value for a certain specific rotating speed. Under the condition of keeping a certain density of the blade cascade, the number of the blades is increased, and the length of the blades is reduced. If blade length is understood to be the distance from the hub to the rim (which depends on the specific speed of the pump), the sweep angle is related to the blade length, the longer the blade the greater the sweep angle.
4. The difference between the impeller blade and the guide vane blade is that the impeller adopts a backswept mode, namely, the blade profile at the wheel edge rotates backwards (by taking the rotation direction of the impeller as the front) by an angle relative to the blade profile at the wheel hub. The guide vane is opposite and is forward-inclined, namely the edge of the guide vane rotates forwards at a certain angle relative to the hub. Of course, if the impeller is forward-inclined and the guide vanes are backward-swept, the damping effect should be the same, but the backward-swept impeller is more suitable from the viewpoint of deformation of the blades after being stressed. Especially for an open impeller, the clearance between the impeller blade and the pump shell is very small, the diameter of the forward-inclined blade is increased after the forward-inclined blade is stressed (including hydrodynamic force and centrifugal force), and the forward-inclined blade is easy to rub the pump shell, so that the safety is influenced.
Drawings
FIG. 1 is a schematic structural view of a conventional impeller blade;
FIG. 2 is a schematic structural view of a conventional guide vane blade;
FIG. 3 is a schematic diagram of the forward pitch of the impeller blades of the present invention;
FIG. 4 is a schematic view of the backswept configuration of the impeller blades of the present invention;
FIG. 5 is a schematic structural view of a guide vane blade of the present invention;
FIG. 6 is a projection of the impeller blades in a plane perpendicular to the pump axis;
FIG. 7 is a comparative isometric view of an impeller blade of the present invention and a conventional impeller blade.
Reference numerals: 1. impeller shaft side picture, 2, impeller blade inlet edge, 3, conventional impeller blade, 4, flow surface, 5, shaft surface streamline, 6, impeller blade outlet edge, 7, conventional impeller blade shaft surface projection, 8, conventional impeller blade plane projection, 9, guide vane shaft side picture, 10, guide vane inlet edge, 11, conventional guide vane blade, 12, conventional guide vane blade shaft surface projection, 13, conventional guide vane plane projection, 14, guide vane outlet edge, 15, impeller blade, 16, impeller blade shaft surface projection, 17, impeller blade plane projection, 18, guide vane blade, 19, guide vane blade shaft surface projection, 20, guide vane blade horizontal projection.
Detailed Description
The technical scheme of the invention is further elaborated in the following by combining the drawings in the specification.
Example 1
Referring to fig. 1-7 of the specification, this embodiment discloses:
fig. 1 and 2 show a conventional impeller blade 3 and a conventional guide vane blade 11, respectively, obtained by conventional methods, since the movement of the liquid in the pump impeller is a complex spatial movement, and in order to simplify the analytical calculations, an assumption is usually introduced that the flow conditions are close to the independence of the flow surface 4. That is, the liquid particles in the impeller flow on a cylindrical surface centered on the pump axis, and the movement of the liquid particles on adjacent cylindrical surfaces is not related to each other, that is, there is no radial component velocity of the liquid particles in the impeller flow region. Therefore, in conventional designs, it is always possible to arrange the impeller blade inlet edge 2 and the impeller blade outlet edge 6, or the guide vane inlet edge 10 and the guide vane outlet edge 14, in the same axial plane. The vane inlet edge is made nearly perpendicular to the water flow direction (as in the relation between the axial streamlines 5 on the axial plane 4 and the conventional impeller vanes 3 in the impeller axial side fig. 1 and guide vane axial side fig. 9 of fig. 1 and 2) so that the radial component of the vane's force on the water flow is small. In the case of different blade wrap angles on the flow surfaces from the hub to the rim, it is not possible to arrange the inlet edges 2, 10 and the outlet edges 6, 14 in one axial plane. However, in view of hydraulic calculation and manufacturability requirements, the designer always considers the inlet edges 2, 10 and the outlet edges 6, 14 together, so that they are each as close as possible to one axial plane. However, the damping effect of the impeller/guide vane blade obtained in this way is not good, and the shape of the impeller blade or guide vane blade proposed in fig. 3 to 5 should be adopted for a product whose primary design objective is to reduce noise.
The blade shape proposed in this embodiment can be (but is not limited to) based on a blade obtained by a conventional design method, and the blade profiles on the flow surfaces 4 from the hub to the rim are sequentially rotated in a circumferential direction by a certain angle relative to the previous blade profile. As shown in fig. 3, 4 and 5, the blade may be a single impeller blade 15, or a single guide vane blade 18, or both the impeller blade 15 and the guide vane blade 18 are formed by rotating the vane profile on each flow surface 4 from the hub to the rim in a circumferential direction at a certain angle with respect to the previous vane profile. As can be seen from the comparison between the conventional impeller blade axial plane projection 7, the conventional impeller blade plane projection 8, the conventional guide vane blade axial plane projection 12, and the conventional guide vane plane projection 13 in fig. 1 and 2 and the impeller blade axial plane projection 16, the impeller blade plane projection 17, the guide vane blade axial plane projection 19, and the guide vane blade horizontal projection 20 in fig. 3, 4, and 5, the blade profile on each flow surface 4 of the impeller blade 15 or the guide vane blade 18 of the present application from the hub to the rim is sequentially rotated by a certain angle in the circumferential direction with respect to the previous blade profile. The larger the relative rotation angle is, the better the vibration damping effect is. However, the process conditions are limited, and the adopted values must be such that the impeller/guide vane blades can be manufactured, and the limit value of the process conditions is gradually reduced along with the development of the 3D printing technology.
Different from the impeller blades and the guide vane blades, the impeller adopts the backswept mode, namely the blade profile at the wheel edge rotates backwards (with the rotating direction of the impeller as the front direction) by an angle relative to the blade profile at the wheel hub (as shown in figure 4). The guide vane is reversed and "forward-tilted" (as shown in fig. 5), i.e., the edge is angled forward relative to the hub. Of course, if the impeller is forward-tilted (as shown in fig. 3) and the vanes are swept backward, the damping effect should be the same, but a swept-backward impeller should be more suitable in view of the deformation of the blades after being stressed. Especially for an open impeller, the clearance between the impeller blade and the pump shell is very small, the diameter of the forward-inclined blade is increased after the forward-inclined blade is stressed (including hydrodynamic force and centrifugal force), and the forward-inclined blade is easy to rub the pump shell, so that the safety is influenced.
The 'certain angle' has no absolute value, and for different design objects, the optimal value can be determined only by complex calculation (CFD analysis) and comprehensive consideration of indexes such as efficiency, cavitation, vibration, strength and the like and the limitation of materials and process conditions. In a trend, the larger the sweep angle, the better the damping effect, but the efficiency, cavitation, etc. are adversely affected, and this effect increases with increasing sweep angle. This effect is not significant when the sweep angle is not too large, but increases with increasing angle. Meanwhile, the larger the angle is, the greater the processing difficulty is, and the strength and rigidity of the blade are weakened. Therefore, for different engineering projects, due to different requirements on efficiency and cavitation indexes and different adopted processing technologies and equipment, the limitation on the sweepback angle is different. In most cases, the optimum sweep angle is approximately 25 to 50 degrees. And the higher the specific speed of the pump, the greater the optimum sweep angle.
As shown in fig. 6, the angle phi is the sweepback angle of the impeller blade, and Δ phi is the angle of relative rotation of the blade profile on the adjacent flow surface. Under the condition of a certain total sweep angle (25-50 degrees), the inlet and outlet edges of the blades form a smooth curve by reasonably distributing delta phi among the blades, and meanwhile, the inlet and outlet edges and the surfaces of the hub and the wheel rim are close to be orthogonal as much as possible at the hub and the wheel rim (for a closed impeller) so as to facilitate processing.
As shown in fig. 7, the profiles on each flow surface of the blade from the hub to the rim are in turn rotated by a certain angle in the circumferential direction with respect to the previous profile, where "in turn" means from the hub to the rim the latter from the rim to the hub. The result is the same except that the direction of rotation is different.
The number of blades, as well as the sweep angle, is limited by efficiency, cavitation, intensity and process conditions, which need to be determined for the specific subject's specifications. In conventional designs, the number of vanes is determined based on the specific speed of the pump. In many cases, the number of blades can be increased by 50% to 100% from the conventional value for vibration damping. The number of blades is not strongly related to the sweep angle, both of which are measures for damping, and when one of the terms is more severely limited, the other term may be considered to be selected to have a relatively large value.
Example 2
As another preferred embodiment of the present invention, referring to fig. 3-5 of the specification, the present embodiment discloses:
a design method of a mixed flow pump for vibration and noise reduction is characterized in that: the method comprises the following steps:
rotating the blade profile of each flow surface of the blade from the hub to the rim of the mixed flow pump in the same direction by the same angle delta phi relative to the previous blade profile in the circumferential direction, wherein the rotating angle phi of the blade profile of the flow surface of the blade at the rim relative to the blade profile of the flow surface of the blade at the hub is 25-50 degrees; increasing the number of blades of the mixed flow pump, wherein the increased number is 50-100% of the number of blades of the same type of conventional mixed flow pump; the blades are impeller blades and/or guide vane blades. The vane profile on each flow surface of the impeller blade from the hub to the rim is sequentially rotated in the circumferential direction relative to the previous vane profile in the opposite direction to the vane profile on each flow surface of the guide vane blade from the hub to the rim.
Example 3
As another preferred embodiment of the present invention, referring to fig. 3-5 of the specification, the present embodiment discloses:
a design method of an axial flow pump for vibration and noise reduction is characterized in that: the method comprises the following steps:
rotating the blade profile of each flow surface of the blades of the axial flow pump from the hub to the rim by the same angle delta phi in the same direction in the circumferential direction relative to the previous blade profile, wherein the rotating angle phi of the blade profile on the flow surface of the blades at the rim relative to the blade profile on the flow surface of the blades at the hub is 25-50 degrees; increasing the number of blades of the axial flow pump, wherein the increased number is 50% -100% of the number of blades of the same type of conventional axial flow pump; the blades are impeller blades and/or guide vane blades. The vane profile on each flow surface of the impeller blade from the hub to the rim is sequentially rotated in the circumferential direction relative to the previous vane profile in the opposite direction to the vane profile on each flow surface of the guide vane blade from the hub to the rim.
Example 4
As another preferred embodiment of the present invention, referring to fig. 3-5 of the specification, the present embodiment discloses:
a design method of a mixed flow pump for vibration and noise reduction is characterized in that: the method comprises the following steps:
rotating the blade profile of each flow surface of the blade from the hub to the rim of the mixed flow pump in the same direction by the same angle delta phi relative to the previous blade profile in the circumferential direction, wherein the rotating angle phi of the blade profile of the flow surface of the blade at the rim relative to the blade profile of the flow surface of the blade at the hub is 25-50 degrees; increasing the number of blades of the mixed flow pump, wherein the increased number is 50-100% of the number of blades of the same type of conventional mixed flow pump; the blades are impeller blades and/or guide vane blades. The vane profile on each flow surface of the impeller blade from the hub to the rim is sequentially rotated in the circumferential direction relative to the previous vane profile in the opposite direction to the vane profile on each flow surface of the guide vane blade from the hub to the rim. The impeller blades are arranged in a backswept mode, specifically, the blade profile at the wheel edge rotates backwards by an angle relative to the blade profile at the wheel hub, and the backward rotation specifically refers to a direction opposite to the rotation direction of the impeller. The guide vane blades are arranged in a forward tilting mode, the forward tilting mode specifically means that the blade profile at the wheel edge rotates forwards by an angle relative to the blade profile at the wheel hub, and the forward rotation specifically means the direction the same as the rotation direction of the impeller.
Example 5
As another preferred embodiment of the present invention, referring to fig. 3-5 of the specification, the present embodiment discloses:
a design method of an axial flow pump for vibration and noise reduction is characterized in that: the method comprises the following steps:
rotating the blade profile of each flow surface of the blades of the axial flow pump from the hub to the rim by the same angle delta phi in the same direction in the circumferential direction relative to the previous blade profile, wherein the rotating angle phi of the blade profile on the flow surface of the blades at the rim relative to the blade profile on the flow surface of the blades at the hub is 25-50 degrees; increasing the number of blades of the axial flow pump, wherein the increased number is 50% -100% of the number of blades of the same type of conventional axial flow pump; the blades are impeller blades and/or guide vane blades. The vane profile on each flow surface of the impeller blade from the hub to the rim is sequentially rotated in the circumferential direction relative to the previous vane profile in the opposite direction to the vane profile on each flow surface of the guide vane blade from the hub to the rim. The impeller blades are arranged in a backswept mode, specifically, the blade profile at the wheel edge rotates backwards by an angle relative to the blade profile at the wheel hub, and the backward rotation specifically refers to a direction opposite to the rotation direction of the impeller. The guide vane blades are arranged in a forward tilting mode, the forward tilting mode specifically means that the blade profile at the wheel edge rotates forwards by an angle relative to the blade profile at the wheel hub, and the forward rotation specifically means the direction the same as the rotation direction of the impeller.
Claims (8)
1. A design method of a mixed flow pump for vibration and noise reduction is characterized in that: the method comprises the following steps:
rotating the blade profile of each flow surface of the blade from the hub to the rim of the mixed flow pump in the same direction by the same angle delta phi relative to the previous blade profile in the circumferential direction, wherein the rotating angle phi of the blade profile of the flow surface of the blade at the rim relative to the blade profile of the flow surface of the blade at the hub is 25-50 degrees;
increasing the number of blades of the mixed flow pump, wherein the increased number is 50-100% of the number of blades of the same type of conventional mixed flow pump;
the blades are impeller blades and/or guide vane blades.
2. A method of designing a vibration and noise reducing mixed flow pump as defined in claim 1, wherein: the vane profile on each flow surface of the impeller blade from the hub to the rim is sequentially rotated in the circumferential direction relative to the previous vane profile in the opposite direction to the vane profile on each flow surface of the guide vane blade from the hub to the rim.
3. A method of designing a vibration and noise reducing mixed flow pump as defined in claim 1, wherein: the impeller blades are arranged in a backswept mode, specifically, the blade profile at the wheel edge rotates backwards by an angle relative to the blade profile at the wheel hub, and the backward rotation specifically refers to a direction opposite to the rotation direction of the impeller.
4. A method for designing a vibration and noise reducing mixed flow pump as defined in claim 1 or 3, wherein: the guide vane blades are arranged in a forward tilting mode, the forward tilting mode specifically means that the blade profile at the wheel edge rotates forwards by an angle relative to the blade profile at the wheel hub, and the forward rotation specifically means the direction the same as the rotation direction of the impeller.
5. A design method of an axial flow pump for vibration and noise reduction is characterized in that: the method comprises the following steps:
rotating the blade profile of each flow surface of the blades of the axial flow pump from the hub to the rim by the same angle delta phi in the same direction in the circumferential direction relative to the previous blade profile, wherein the rotating angle phi of the blade profile on the flow surface of the blades at the rim relative to the blade profile on the flow surface of the blades at the hub is 25-50 degrees;
increasing the number of blades of the axial flow pump, wherein the increased number is 50% -100% of the number of blades of the same type of conventional axial flow pump;
the blades are impeller blades and/or guide vane blades.
6. The design method of the vibration and noise reduction axial flow pump according to claim 5, characterized in that: the vane profile on each flow surface of the impeller blade from the hub to the rim is sequentially rotated in the circumferential direction relative to the previous vane profile in the opposite direction to the vane profile on each flow surface of the guide vane blade from the hub to the rim.
7. The design method of the vibration and noise reduction axial flow pump according to claim 5, characterized in that: the impeller blades are arranged in a backswept mode, specifically, the blade profile at the wheel edge rotates backwards by an angle relative to the blade profile at the wheel hub, and the backward rotation specifically refers to a direction opposite to the rotation direction of the impeller.
8. A method of designing a vibration and noise reducing axial flow pump according to claim 5 or 7, wherein: the guide vane blades are arranged in a forward tilting mode, the forward tilting mode specifically means that the blade profile at the wheel edge rotates forwards by an angle relative to the blade profile at the wheel hub, and the forward rotation specifically means the direction the same as the rotation direction of the impeller.
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN112879341A (en) * | 2021-01-22 | 2021-06-01 | 兰州理工大学 | High-cavitation-resistance backswept and split-flow offset type spiral centrifugal impeller |
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