CN110513326B - Centrifugal pump impeller capable of actively controlling pressure pulsation - Google Patents
Centrifugal pump impeller capable of actively controlling pressure pulsation Download PDFInfo
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- CN110513326B CN110513326B CN201910793510.1A CN201910793510A CN110513326B CN 110513326 B CN110513326 B CN 110513326B CN 201910793510 A CN201910793510 A CN 201910793510A CN 110513326 B CN110513326 B CN 110513326B
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- blade
- cover plate
- centrifugal pump
- front cover
- rear cover
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- 230000010349 pulsation Effects 0.000 title claims abstract description 34
- 238000000034 method Methods 0.000 claims abstract description 5
- 230000007704 transition Effects 0.000 claims description 4
- 230000007423 decrease Effects 0.000 claims description 3
- 239000012530 fluid Substances 0.000 abstract description 4
- 238000011160 research Methods 0.000 description 5
- 230000003068 static effect Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 241000283153 Cetacea Species 0.000 description 3
- 238000005192 partition Methods 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 238000002347 injection Methods 0.000 description 2
- 239000007924 injection Substances 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000009792 diffusion process Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000011664 nicotinic acid Substances 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
Classifications
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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
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2261—Rotors specially for centrifugal pumps with special measures
- F04D29/2272—Rotors specially for centrifugal pumps with special measures for influencing flow or boundary layer
-
- 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
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/24—Vanes
- F04D29/242—Geometry, shape
- F04D29/245—Geometry, shape for special effects
-
- 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
Abstract
The present invention relates to the field of fluid machinery. The technical proposal is as follows: an impeller of a centrifugal pump for actively controlling pressure pulsation comprises a front cover plate with an inlet, a rear cover plate with a shaft sleeve and a plurality of blades arranged between the front cover plate and the rear cover plate; the front cover plate and the rear cover plate are both revolved bodies taking the rotation axis as a central line, and the plurality of blades are uniformly distributed between the front cover plate and the rear cover plate; each blade is bent into an arc shape, the width direction of each blade is parallel to the rotation axis, two sides of the width direction of each blade are respectively clung to the inner surface of the front cover plate and the inner surface of the rear cover plate, and two ends of the length direction of each blade are respectively clung to the outer edges of the shaft sleeve and the revolving body; the method is characterized in that: the tail edge profile of the blade at one end of the outer edge of the revolving body is wavy, and a plurality of diversion trenches arranged along the width direction of the blade are arranged on the suction surface of the blade. The impeller can effectively weaken the intensity of the falling vortex, and improve the pressure pulsation performance of the whole pump and the safety of the operation of the pump.
Description
Technical Field
The invention relates to the field of fluid machinery, in particular to a centrifugal pump impeller capable of actively controlling pressure pulsation.
Background
The centrifugal pump is used as an important fluid conveying device and is widely applied to the fields of urban water supply, navigation, aviation, fire fighting and other national economy. The flow in the centrifugal pump is complex three-dimensional, viscous and unsteady flow due to the reasons of flow channel diffusion, vane distortion, high-speed rotation, interference of dynamic and static components and the like, and complex flow phenomenon exists; such as backflow of an inlet and an outlet, cavitation, dynamic and static interference, rotating stall and the like in the running process of the centrifugal pump, the flow phenomena can be accompanied by the generation of pressure pulsation, the pressure pulsation amplitude at the outlet end of the blade is large, the pulsation frequency is complex, and the pressure pulsation is an important factor affecting the stable running of the impeller. When the impeller sweeps the partition tongue, the fluid at the outlet end of the blade performs periodical impact on the partition tongue of the guide vane or the volute, periodical wake vortex shedding is generated, so that the high-strength wake vortex at the outlet end of the blade has remarkable influence on the pressure pulsation performance of the pump, and further the movement performance of the whole pump is directly influenced. Therefore, the optimization design is carried out for the impeller outlet structure, and the method has important significance for improving the pump pressure pulsation performance.
There has been much research on the pressure pulsation performance of centrifugal pumps. Khalifa in the research of Exploring THE EFFECT of V-Profiled Cut at Blade Exit of a Double Volute Centrifugal Pump, V-shaped cutting is carried out on the outlet tail edge of the blade, wherein the V-shaped cutting comprises a suction surface and a pressure surface, so that the effective gap between the impeller and the partition tongue is increased, the pressure pulsation caused by dynamic and static interference is reduced, and the external characteristics of the pump can be obviously reduced; chinese patent No. 201711361217.5 discloses a centrifugal pump impeller with low pressure pulsation performance, which is characterized in that the periodic wake vortex shedding intensity at the outlet end of the impeller is restrained by arranging injection slits on the impeller blades and penetrating through the blades, so that the low pressure pulsation characteristic is obtained; but the injection flow increases the hydraulic loss of the impeller and reduces the hydraulic efficiency of the centrifugal pump.
Disclosure of Invention
The invention aims to overcome the defects of the prior art, and provides an improvement of a centrifugal pump impeller capable of actively controlling pressure pulsation, which can effectively weaken the intensity of falling vortex, improve the falling structure of wake vortex, lead the flow of an impeller outlet to be smooth, reduce the dynamic and static interference effect of a tongue isolation area, and improve the pressure pulsation performance of the whole pump, the external characteristics, the safety and the stability of the pump operation.
The technical scheme provided by the invention is as follows: an impeller of a centrifugal pump for actively controlling pressure pulsation comprises a front cover plate with an inlet, a rear cover plate with a shaft sleeve and a plurality of blades arranged between the front cover plate and the rear cover plate; the front cover plate and the rear cover plate are both revolved bodies taking the rotation axis as a central line, and the plurality of blades are uniformly distributed between the front cover plate and the rear cover plate; each blade is bent into an arc shape, the width direction of each blade is parallel to the rotation axis, two sides of the width direction of each blade are respectively clung to the inner surface of the front cover plate and the inner surface of the rear cover plate, and two ends of the length direction of each blade are respectively clung to the outer edges of the shaft sleeve and the revolving body; the method is characterized in that: the tail edge profile of the blade at one end of the outer edge of the revolving body is wavy, and a plurality of diversion trenches arranged along the width direction of the blade are arranged on the suction surface of the blade; the cross section profile of each diversion trench is sinusoidal, and smoothly transits from the tail edge to the other end of the blade, and the trench depth of each diversion trench gradually decreases to the direction of the other end of the blade until the trench depth is zero;
the length L of the diversion trench is determined according to the following formula:
L＝k*B2，
wherein: k is a transition coefficient, the value range of k is 1-5, and B 2 is the width of the tail edge of the blade;
Blade trailing edge width B 2 is calculated according to the following formula:
Wherein:
n-the rated rotational speed of the centrifugal pump, unit r/min;
Q-rated flow of centrifugal pump, unit m 3/s;
H is the rated lift of the centrifugal pump, and the unit is m.
Preferably, the wavy curve is a linear sinusoidal curve, and satisfies a functional relationship:
Wherein: is the initial phase.
The wave-shaped amplitude A is less than or equal to 0.3 x B 2, and the wavelength lambda is less than or equal to 0.5 x B 2.
The distance between the front cover plate and the rear cover plate gradually increases from the edge of the revolving body to the axis direction of the revolving body; the width of the blade is adapted to this.
The working principle of the invention is as follows: according to the bionic principle, the large vortex of the wake is dispersed into the small vortex by the trailing edge structure of the outlet of the suction surface of the impeller blade, so that the low pressure pulsation characteristic of the pump is realized. Meanwhile, under the combined action of the blade tail edge and the diversion trench structure, the falling structure and strength of wake vortex in the outlet area and the flow separation phenomenon in the area are limited, so that the speed distribution of the near wall surface is more uniform, and the hydraulic loss of the centrifugal pump is reduced.
The beneficial effects of the invention are as follows: the trailing edge structure and the diversion trench structure of the blade suction surface outlet are optimized, so that the high-strength wake large vortex is dispersed into a plurality of small vortices, the structure of the trailing edge shedding vortex is effectively improved, the strength of the shedding vortex is weakened, the flow of the impeller outlet is relatively gentle, the dynamic and static interference effect of the impeller outlet is reduced, the hydraulic loss of the pump is reduced, and the pressure pulsation performance of the whole pump is improved.
Drawings
FIG. 1 is a schematic three-dimensional structure of an embodiment of the present invention.
Fig. 2 is an axial cross-sectional projection of an embodiment of the present invention.
Fig. 3 is a plan projection view of an embodiment of the present invention.
Fig. 4 is a schematic perspective view of a blade according to an embodiment of the present invention.
FIG. 5 is an enlarged schematic view of the trailing edge of a blade in an embodiment of the invention.
Fig. 6 is a frequency domain analysis of pressure pulsations at the original impeller and the diaphragm of an embodiment of the present invention.
Reference numerals in the drawings: 1-a front cover plate; 2-a rear cover plate; 3-leaves; 4-trailing edge; 5-blade inlet end; 6, blade outlet end; 7, a pressure surface; 8, a suction surface; 9-diversion trench.
Detailed Description
The design of the new impeller is described in detail below with reference to the drawings and specific examples. The present embodiment is only for further description of the present invention, but should not be construed as limiting the protection of the present invention, and some insubstantial modifications to the above-described invention by those skilled in the art are within the scope of the protection of the present invention.
In combination with the accompanying drawings, the embodiment is a closed impeller of a centrifugal pump (for comparison, the invention improves on the prior closed impeller of the centrifugal pump), but the semi-open impeller and the open impeller are also applicable. Fig. 1 to 3 show a schematic structural view of the impeller, which comprises a front cover plate 1, a rear cover plate 2 and a plurality of blades 3 arranged between the front cover plate and the rear cover plate. The pressure surface 7 and the suction surface 8 of the blade are formed by smoothly connecting a plurality of arc surfaces, and the number of the blades is 5. These are the same as the prior closed impeller of the centrifugal pump.
According to researches, although the whale sitting head has huge body size, the whale sitting head has excellent maneuvering performance, and related expert researches find that the fin-shaped limb front edge of the whale sitting head is uniformly provided with a protruding structure, and the structure has excellent hydrodynamic performance, so that a good effect is obtained on the dynamics research of the hydrofoil. For this purpose, the invention envisages the trailing edge 4 profile of the blade at the outlet of the suction surface 8 (as in fig. 1) to be wavy; and the wavy curve is preferably a linear sinusoidal curve (see fig. 5) and satisfies a functional relationship:
Wherein: ("x" means the number of the multiplier, the following is the same)
A-amplitude, A is less than or equal to 0.3 x B 2, and the longitudinal height of the sinusoidal protruding structure of the trailing edge 4 of the blade is shown on the impeller;
Lambda-sine wavelength, lambda is less than or equal to 0.5 x B 2, and the transverse period length of the sine protuberance structure of the tail edge 4 of the blade is shown on the impeller;
-an initial phase; in this embodiment/>
The coordinate system is constructed in the following way (see fig. 2):
Taking the intersection point of the impeller front cover plate 1 and the outlet edge of the blade suction surface 8 as an origin (0, 0); the direction of the x axis is the direction that the impeller front cover plate 1 points to the rear cover plate 2 (the x axis is parallel to the impeller axis); the y-axis is oriented in a radial direction perpendicular to the impeller axis. The values of A and lambda directly influence the structure and strength of the shedding vortex.
Meanwhile, the outlet part of the suction surface 8 of the blade is also provided with a plurality of diversion trenches 9 (see fig. 4), and the diversion trenches 9 are uniformly arranged along the axial direction of the blade (i.e. the width direction of the blade). Under the combined action of the vane tail edge 4 and the diversion trench 9, the structure and the strength of wake vortex shedding in the outlet area and the flow separation phenomenon in the area are limited, so that the water flow velocity distribution of the near-wall surface is more uniform, and the hydraulic loss of the centrifugal pump is reduced. Each diversion trench 9 takes the tail edge profile as an initial profile, and smoothly transits from the tail edge 4 of the blade to the direction of the inlet end 5 of the blade, and the trench depth gradually decreases until zero. The flow guide grooves 9 are mutually parallel, the cross sections of the flow guide grooves are sine-shaped, the number of the flow guide grooves 9 is the same as that of the wave troughs of the sine-shaped structure of the blade tail edge 4, and the number of the wave troughs is not less than 1. The transition length of the diversion trench 9 along the suction surface 8 of the blade is L, the relation L=k is satisfied, B 2, k is a transition coefficient, and the value range of k is 1-5; b 2 is the blade outlet end 6 width (i.e. blade trailing edge width). The value of k is selected according to the width B 2 of the blade outlet end 6.
The blade trailing edge width B 2 (i.e., blade outlet end width) can be calculated according to the following formula:
Wherein:
n-rated rotation speed of centrifugal pump, the unit is r/min;
q-rated flow of centrifugal pump, unit is m 3/s;
h, the rated lift of the centrifugal pump, and the unit is m.
In this embodiment, according to the design requirements (the rated rotation speed n of the centrifugal pump, the rated flow Q of the centrifugal pump, and the rated lift H of the centrifugal pump), the width B 2 of the blade outlet end 6 is calculated to be 0.01m, and the amplitude a=0.1×b 2 of the sinusoidal protruding structure is calculated to be 0.001m; the period length lambda=0.25×b 2 of the sinusoidal protruding structure takes a value of 0.0025m; the length l= 1*B 2 of the diversion trench 9 takes a value of 0.01m.
The invention compares the pressure pulsation of the novel impeller of the centrifugal pump designed by adopting the blade at the cutting tongue with the pressure pulsation of the original impeller (see figure 6); it is apparent from this figure that the pressure pulsation amplitude of the novel impeller of the present invention at each primary frequency is lower than that of the original impeller. Wherein at the first main frequency (blade frequency), the pressure amplitude of the original impeller is 11931.6Pa, the pressure pulsation amplitude of the novel impeller is 10104.6Pa, and the pressure pulsation amplitude of the novel impeller is reduced by 12.8% compared with that of the original impeller. Therefore, the novel impeller of the centrifugal pump for actively controlling the pressure pulsation provided by the invention obviously reduces the pressure pulsation of the centrifugal pump, improves the pressure pulsation performance of the centrifugal pump, ensures the running stability and safety of the whole pump, and achieves the expected (pressure pulsation reducing) purpose.
Claims (4)
1. An impeller of a centrifugal pump for actively controlling pressure pulsation comprises a front cover plate (1) with an inlet, a rear cover plate (2) with a shaft sleeve and a plurality of blades (3) arranged between the front cover plate and the rear cover plate; the front cover plate and the rear cover plate are both revolved bodies taking the rotation axis as a central line, and the plurality of blades are uniformly distributed between the front cover plate and the rear cover plate; each blade is bent into an arc shape, the width direction of each blade is parallel to the rotation axis, two sides of the width direction of each blade are respectively clung to the inner surface of the front cover plate and the inner surface of the rear cover plate, and two ends of the length direction of each blade are respectively clung to the outer edges of the shaft sleeve and the revolving body; the method is characterized in that: the profile of a tail edge (4) of the blade at one end of the outer edge of the revolving body is wavy, and a plurality of diversion trenches (9) which are arranged along the width direction of the blade are arranged on a suction surface (8) of the blade; the cross section profile of each diversion trench is sinusoidal, and smoothly transits from the tail edge to the other end of the blade, and the trench depth of each diversion trench gradually decreases to the direction of the other end of the blade until the trench depth is zero;
the length L of the diversion trench is determined according to the following formula:
L＝k*B2，
wherein: k is a transition coefficient, the value range of k is 1-5, and B 2 is the width of the tail edge of the blade;
Blade trailing edge width B 2 is calculated according to the following formula:
Wherein:
n-the rated rotational speed of the centrifugal pump, unit r/min;
Q-rated flow of centrifugal pump, unit m 3/s;
H is the rated lift of the centrifugal pump, and the unit is m.
2. The centrifugal pump impeller of claim 1, wherein the centrifugal pump impeller actively controls pressure pulsations, wherein: the wavy curve is a linear sinusoidal curve and satisfies the functional relation: Wherein: /(I) Is the initial phase.
3. The centrifugal pump impeller of claim 2, wherein the centrifugal pump impeller actively controls pressure pulsation, wherein: the wave-shaped amplitude A is less than or equal to 0.3 x B 2, and the wavelength lambda is less than or equal to 0.5 x B 2.
4. A centrifugal pump impeller for active control of pressure pulsations according to claim 3, characterized in that: the distance between the front cover plate and the rear cover plate gradually increases from the edge of the revolving body to the axis direction of the revolving body; the width of the blade is adapted to this.
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| CN112682350B (en) * | 2020-12-16 | 2023-08-18 | 安徽工程大学 | Design method for thickness of impeller blade of centrifugal pump |
| CN113553671B (en) * | 2021-07-08 | 2022-07-08 | 浙江大学 | Bionic anti-cavitation axial flow impeller design method |
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