CN212508963U - Mixed flow pump or axial flow pump - Google Patents
Mixed flow pump or axial flow pump Download PDFInfo
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- CN212508963U CN212508963U CN202021174445.9U CN202021174445U CN212508963U CN 212508963 U CN212508963 U CN 212508963U CN 202021174445 U CN202021174445 U CN 202021174445U CN 212508963 U CN212508963 U CN 212508963U
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Abstract
The utility model discloses a mixed flow pump or axial-flow pump relates to hydroelectric power generation equipment technical field. The mixed flow pump or axial flow pump of the utility model comprises blades, wherein the blade profile on each flow surface of the blade from the hub to the wheel rim rotates in the same direction and at the same angle relative to the previous blade profile in the circumferential direction; the rotating angle of the blade profile on the flow surface of the blade at the wheel edge is 25-50 degrees relative to the blade profile on the flow surface of the blade at the wheel hub; the blades are impeller blades and/or guide vane blades. The utility model provides a novel design of blade shape can (but not limited to) be based on the blade that traditional design method gained, will follow the profile on wheel hub to each flow surface of rim and rotate certain angle in the circumferencial direction for last profile in proper order. 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 utility model relates to a hydroelectric equipment technical field, more specifically say and relate to a 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.
SUMMERY OF THE UTILITY MODEL
In order to overcome the defect and not enough that exist among the above-mentioned prior art, the utility model provides a mixed flow pump, the utility model discloses an invention aim at solves among the prior art "mixed flow pump blade design damping effect not good, can't satisfy the problem to the higher product of noise requirement". The utility model provides a novel design of blade shape can (but not limited to) be based on the blade that traditional design method gained, will follow the profile on wheel hub to each flow surface of rim and rotate certain angle in the circumferencial direction for last profile in proper order. 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 existing in the prior art, the utility model discloses a realize through following technical scheme:
a mixed flow pump comprising a vane, characterized in that: the blade profiles on the flow surfaces of the blades from the hub to the rim rotate in the same direction and at the same angle relative to the previous blade profile in the circumferential direction in sequence; the rotating angle of the blade profile on the flow surface of the blade at the wheel edge is 25-50 degrees relative to the blade profile on the flow surface of the blade at the wheel hub; 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 utility model also provides an axial-flow pump, solve among the prior art "axial-flow pump blade design damping effect not good, can't satisfy the problem to the higher product of noise requirement". The utility model provides a novel design of blade shape can (but not limited to) be based on the blade that traditional design method gained, will follow the profile on wheel hub to each flow surface of rim and rotate certain angle in the circumferencial direction for last profile in proper order. The hydraulic vibration of the pump is obviously low, the vibration reduction effect of the product is obvious, and the noise is low.
An axial-flow pump, includes the blade, its characterized in that: the blade profiles on the flow surfaces of the blades from the hub to the rim rotate in the same direction and at the same angle relative to the previous blade profile in the circumferential direction in sequence; the rotating angle of the blade profile on the flow surface of the blade at the wheel edge is 25-50 degrees relative to the blade profile on the flow surface of the blade at the wheel hub; 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 utility model discloses profitable technological effect who brings shows:
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 structural view of the impeller blade of the present invention leaning forward;
FIG. 4 is a schematic view of the sweepback structure of the impeller blade of the present invention;
fig. 5 is a schematic structural view of the 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 side view of an impeller blade of the present invention in comparison to a conventional impeller blade.
Reference numerals: 1. impeller, 2, impeller blade inlet edge, 3, conventional impeller blade, 4, flow surface, 5, axial surface streamline, 6, impeller blade outlet edge, 7, conventional impeller blade axial surface projection, 8, conventional impeller blade plane projection, 9, guide vane, 10, guide vane inlet edge, 11, conventional guide vane blade, 12, conventional guide vane blade axial surface projection, 13, conventional guide vane plane projection, 14, guide vane outlet edge, 15, impeller blade, 16, impeller blade axial surface projection, 17, impeller blade plane projection, 18, guide vane blade, 19, guide vane blade axial surface projection, 20, guide vane blade horizontal projection.
Detailed Description
The technical solution of the present invention will be further elaborated with reference to the drawings attached to the description.
Example 1
As a preferred embodiment of the present invention, referring to fig. 1-7 of the specification, the present 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 blade inlet edge is made nearly perpendicular to the water flow direction (as in the relation between the axial streamlines 5 on the flow surface 4 and the conventional impeller blades 3 of the impeller 1 and the guide vane 9 in fig. 1 and 2), so that the radial component of the force of the blades 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 mixed flow pump comprises blades, wherein each blade profile on each flow surface of the blades from a hub to a rim sequentially rotates at the same angle in the same direction in the circumferential direction relative to the previous blade profile; the rotating angle of the blade profile on the flow surface of the blade at the wheel edge is 25-50 degrees relative to the blade profile on the flow surface of the blade at the wheel hub; 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:
an axial flow pump comprises blades, wherein the blades on each flow surface from a hub to a rim sequentially rotate at the same angle in the same direction in the circumferential direction relative to the previous blade; the rotating angle of the blade profile on the flow surface of the blade at the wheel edge is 25-50 degrees relative to the blade profile on the flow surface of the blade at the wheel hub; 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 mixed flow pump comprises blades, wherein each blade profile on each flow surface of the blades from a hub to a rim sequentially rotates at the same angle in the same direction in the circumferential direction relative to the previous blade profile; the rotating angle of the blade profile on the flow surface of the blade at the wheel edge is 25-50 degrees relative to the blade profile on the flow surface of the blade at the wheel hub; 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:
an axial flow pump comprises blades, wherein the blades on each flow surface from a hub to a rim sequentially rotate at the same angle in the same direction in the circumferential direction relative to the previous blade; the rotating angle of the blade profile on the flow surface of the blade at the wheel edge is 25-50 degrees relative to the blade profile on the flow surface of the blade at the wheel hub; 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 mixed flow pump comprising a vane, characterized in that: the blade profiles on the flow surfaces of the blades from the hub to the rim rotate in the same direction and at the same angle relative to the previous blade profile in the circumferential direction in sequence; the rotating angle of the blade profile on the flow surface of the blade at the wheel edge is 25-50 degrees relative to the blade profile on the flow surface of the blade at the wheel hub; the blades are impeller blades and/or guide vane blades.
2. A mixed flow pump as claimed 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 mixed flow pump as claimed 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 mixed flow pump as claimed 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. An axial-flow pump, includes the blade, its characterized in that: the blade profiles on the flow surfaces of the blades from the hub to the rim rotate in the same direction and at the same angle relative to the previous blade profile in the circumferential direction in sequence; the rotating angle of the blade profile on the flow surface of the blade at the wheel edge is 25-50 degrees relative to the blade profile on the flow surface of the blade at the wheel hub; the blades are impeller blades and/or guide vane blades.
6. The axial flow pump of claim 5, 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.
7. The axial flow pump of claim 5, 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.
8. An 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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| Application Number | Priority Date | Filing Date | Title |
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| CN202021174445.9U CN212508963U (en) | 2020-06-23 | 2020-06-23 | Mixed flow pump or axial flow pump |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021174445.9U CN212508963U (en) | 2020-06-23 | 2020-06-23 | Mixed flow pump or axial flow pump |
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| CN212508963U true CN212508963U (en) | 2021-02-09 |
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| CN202021174445.9U Active CN212508963U (en) | 2020-06-23 | 2020-06-23 | Mixed flow pump or axial flow pump |
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