CN114076103B - Wear-resistant design method for centrifugal mud pump - Google Patents
Wear-resistant design method for centrifugal mud pump Download PDFInfo
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- CN114076103B CN114076103B CN202110511864.XA CN202110511864A CN114076103B CN 114076103 B CN114076103 B CN 114076103B CN 202110511864 A CN202110511864 A CN 202110511864A CN 114076103 B CN114076103 B CN 114076103B
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- 238000000034 method Methods 0.000 title claims abstract description 18
- 238000013461 design Methods 0.000 title description 8
- 238000011010 flushing procedure Methods 0.000 claims abstract description 48
- 238000005299 abrasion Methods 0.000 claims abstract description 29
- 239000004570 mortar (masonry) Substances 0.000 claims abstract description 19
- 230000002441 reversible effect Effects 0.000 claims abstract description 8
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 28
- 238000007789 sealing Methods 0.000 claims description 6
- 230000015572 biosynthetic process Effects 0.000 claims description 2
- 239000002002 slurry Substances 0.000 abstract description 16
- 230000000694 effects Effects 0.000 description 11
- 238000009792 diffusion process Methods 0.000 description 7
- 239000007787 solid Substances 0.000 description 6
- 239000012530 fluid Substances 0.000 description 5
- 230000009471 action Effects 0.000 description 3
- 230000004888 barrier function Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- 230000002730 additional effect Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000004576 sand Substances 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 230000003116 impacting effect Effects 0.000 description 1
- 230000001788 irregular Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000010534 mechanism of action Effects 0.000 description 1
- 238000005065 mining Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 238000004080 punching Methods 0.000 description 1
- 239000011435 rock Substances 0.000 description 1
- 239000010865 sewage Substances 0.000 description 1
- 239000002689 soil Substances 0.000 description 1
- 239000004575 stone Substances 0.000 description 1
- 239000000126 substance Substances 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
- F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
- F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
- F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous
- F04D7/045—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous with means for comminuting, mixing stirring or otherwise treating
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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
- F04D29/2294—Rotors specially for centrifugal pumps with special measures for protection, e.g. against abrasion
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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
- F04D29/24—Vanes
- F04D29/242—Geometry, shape
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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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
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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
- F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
- F04D29/708—Suction grids; Strainers; Dust separation; Cleaning specially for liquid pumps
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The antiwear method applied to the centrifugal mud pump is characterized by comprising the following steps of: a guide vane is designed on an inlet anti-abrasion ring of the impeller, and a strategy of dividing the mud mortar in advance is adopted to deviate and guide the mud mortar, so that the head of the impeller is prevented from bearing the direct impact of the mud mortar; the guide vanes are arranged on an inlet anti-wear ring of the impeller, a plurality of guide vanes are uniformly distributed on the inner wall of the inlet anti-wear ring in the circumferential direction, and the guide vanes and the inlet anti-wear ring synchronously rotate along with the impeller; meanwhile, the drainage guide vane (2) on the inlet anti-abrasion ring and the corresponding vane are divided into two bodies, and a spacing area B exists; meanwhile, a high-pressure flushing structure is designed on the blade (4), the high-pressure flushing structure is matched with the guide vane (2), a countercurrent jet flow is formed from the blade head (4.1), a reverse pressure gradient is formed, so that the slurry is deviated in advance, even the slurry vortex is prevented from being formed in the interval area B, and finally the slurry is prevented from striking and wearing the blade head (4.1).
Description
Technical Field
The application relates to a wear-resistant design method of a centrifugal mud pump (slurry pump).
Background
The mud pump (also called as slurry pump) is a mechanical device for realizing continuous conveying of substances such as soil, gravel, crushed ore and the like in a pumping mode, is commonly used in the fields of dredging, hydraulic filling, mining machinery, sewage treatment and the like, and is mainly used for applying work to solid particle-water mixtures such as slurry and the like, improving the mechanical energy of the solid particle-water mixtures and conveying the solid particle-water mixtures to a designated area through a pipeline, thus being essential key equipment in the dredging field.
In consideration of various requirements such as convenience in assembly and disassembly, high lift, high efficiency and the like, a single-stage single-suction centrifugal pump is commonly adopted for a mud pump, and a closed impeller structure is commonly adopted for an impeller. In such pumps, fluid is drawn into the pump horizontally from the shaft end, then enters the impeller in rotational motion to flow radially, and is constrained to rotate with the impeller in a flow passage defined by the front and rear cover plates and the blades, in the process, receives the blades to apply work to the fluid to have higher pressure and speed, then flows out of the impeller into a diffusion chamber, is reduced in speed and pressurized in the diffusion chamber, converts part of kinetic energy into pressure energy, and finally flows out of an outlet of the diffusion chamber.
Unlike conventional pumps, the materials delivered by the mud pump (fig. 1) have various irregular and sharp solids, which can cause serious wear to the impeller, the main working part in the mud pump. The problem of wear of the impeller of the dredge pump is still a problem to be solved. The abrasion of the impeller is effectively reduced, the service life of the impeller can be prolonged, and the maintenance cost is saved. Meanwhile, the impeller structure which is as good as possible is a necessary guarantee for the stable operation of the dredge pump and the efficient dredging construction. The main technical approach for reducing the impeller wear is divided into two directions of 'selecting wear-resistant materials' and 'improving structures'.
Closest to the prior art:
at present, the structural design of the impeller of the dredge pump improves the flow in the impeller by reasonably selecting the inlet angle and the wrap angle of the impeller, adopting the technical means of bending and twisting the shape of the impeller and the like, and the structural techniques achieve good results on improving the abrasion, but have no breakthrough development. For the abrasion near the inlet and outlet of the impeller, the suction inlet anti-abrasion ring is generally arranged at the inlet of the impeller, the shoulder blade anti-abrasion ring is arranged outside the outlet of the impeller (specifically, the shoulder blade anti-abrasion ring is arranged between the diffusion chamber and the pump cover and protects the connection part of the diffusion chamber and the pump cover), the abrasion ring is replaced continuously to prevent the local damage of the part from leading to the scrapping of the whole impeller, but the abrasion near the head part of the impeller, the end face near the head part of the impeller and the tail part of the impeller does not have a specific structural improvement technical scheme.
Disclosure of Invention
The application aims to disclose an antiwear method for solving the problem that the serious abrasion of a mud pump mainly occurs in the inlet of an impeller and the head of a blade (mainly near the large radius of a front cover plate).
The abrasion of the blade heads is mainly impact abrasion, because the area of the impeller inlet close to the front cover plate (as in the position of A in fig. 1) has larger circumferential speed, the equal volume of sand, rock blocks is larger, and thus, after the solid with larger hardness enters the impeller, the solid can impact the position (in the position of A in fig. 1) under the action of inertia; therefore, abrasion on the end face near the blade head is often generated by vortex flow, the nearby flow is easy to generate vortex flow due to the diversion effect of the blade head, and sand and stone are repeatedly scraped and rubbed in the vortex flow to cause abrasion.
In order to solve the technical problems, the technical scheme of the application to be protected is as follows:
the antiwear method applied to the centrifugal mud pump is characterized by comprising the following steps of:
a guide vane is designed on an inlet anti-abrasion ring of the impeller, and a strategy of dividing the mud mortar in advance is adopted to deviate and guide the mud mortar, so that the head of the impeller is prevented from bearing the direct impact of the mud mortar; the guide vanes 2 are arranged on an inlet anti-wear ring 1 of the impeller, the guide vanes 2 are uniformly distributed on the inner wall of the inlet anti-wear ring 1 in the circumferential direction, and the guide vanes 2 and the inlet anti-wear ring 1 synchronously rotate along with the impeller;
meanwhile, the drainage guide vane (2) on the inlet anti-wear ring 1 and the corresponding vane 4 are divided into two bodies, and a spacing area B exists;
meanwhile, a high-pressure flushing structure is designed on the blade (4), the high-pressure flushing structure is matched with the guide vane (2), a countercurrent jet flow is formed from the blade head (4.1), a reverse pressure gradient is formed, so that the slurry is deviated in advance, even the slurry vortex is prevented from being formed in the interval area B, and finally the slurry is prevented from striking and wearing the blade head (4.1).
Further limiting the technical proposal, in the impeller, the number of the drainage guide vanes 2 is consistent with that of the blades 4, and the arrangement positions of the drainage guide vanes are opposite to the blades 4, and gaps are reserved between the drainage guide vanes and the blades.
Further defining the technical solution, the guide vane 2 is close to and opposite to the head of the impeller blade 4.
Further limiting the technical scheme, connecting high-pressure water source and high-pressure sealing water between the impeller front cover plate (3) and the front pump cover and the lining plate (12) thereof in the blades through the high-pressure flushing inlet pipe (13), opening flushing holes/grooves (6) on the surfaces of the blade heads (4.1), enabling high-pressure flushing to flow out of the surfaces of the blade heads (4.1) through the flushing holes/grooves (6), forming a reverse pressure gradient in a clearance area (B in fig. 4 and 6) between the blades and the guide vanes, and injecting along the tail parts (2.2) of the guide vanes.
The flushing hole/groove (6) is communicated with the high-pressure sealing water through a water guide pipe (7). Namely, the pressure flushing mechanism is designed and comprises a high-pressure flushing inlet pipe (13), a water guide pipe (7) and a flushing hole/groove (6), wherein the outlet end of the high-pressure flushing inlet pipe (13) is high-pressure sealing water between an impeller front cover plate (3) and a front pump cover and between the impeller front cover plate and a lining plate (12) of the front pump cover plate, and the high-pressure sealing water is connected with the flushing hole/groove (6) through the water guide pipe (7). The flushing hole/groove (6) is arranged on the surface of the blade head (4.1) so that high-pressure flushing water is sprayed out of the blade head (4.1) and forms countercurrent jet flow.
Drawings
FIG. 1 is a side view of a conventional mud pump impeller;
FIG. 2 is a schematic 1/4 section view of the mud pump impeller assembly of example 1;
FIG. 3 is a schematic view of the embodiment 1 impeller assembly and inlet wear ring (with guide vanes installed) rear construction;
FIG. 4 is a schematic illustration of the mechanism of action of the inlet wear ring (mounting the guide vanes) in the impeller assembly of example 1;
fig. 5 example 2 is a side view of a mud pump: illustrating the arrangement and location of the high pressure flush structure;
FIG. 6 embodiment 2 is a schematic illustration of the wear protection of a high pressure flush of a drainage vane and blade head;
numerical marking: 1. an inlet wear ring; 2. a drainage guide vane; 2.1 guide vane head; 2.2 guide vane tail; 3. an impeller front cover plate; 4. impeller blades; 4.1 blade head; 4.2 blade tail;
5. an impeller back cover plate;6. flushing hole (groove)；7. Water guide pipeThe method comprises the steps of carrying out a first treatment on the surface of the 8. A blade working surface; 9. the back of the blade; 10. a pump intake; 11. diffusion chamber wall surfaces; 12. a front pump cover and a liner plate thereof; 13. a high pressure flush inlet pipe.
Detailed Description
The technical scheme provided by the application is further described below with reference to specific embodiments and attached drawings. The advantages and features of the present application will become more apparent in conjunction with the following description.
It should be noted that the embodiments of the present application are preferred embodiments, and are not intended to limit the present application in any way. The technical features or combinations of technical features described in the embodiments of the present application should not be regarded as isolated, and they may be combined with each other to achieve a better technical effect. Additional implementations are also included within the scope of the preferred embodiments of the present application and should be understood by those skilled in the art to which the embodiments of the present application pertain.
Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but should be considered part of the specification where appropriate. In all examples shown and discussed herein, any specific values should be construed as merely illustrative and not limitative. Thus, other examples of the exemplary embodiments may have different values.
The drawings of the application are in a very simplified form and are not to scale precisely, but are for the purpose of illustrating embodiments of the application conveniently and clearly, and are not intended to limit the scope of the application. Any structural modification, proportional change or size adjustment should fall within the scope of the technical disclosure without affecting the effects and the achieved objects of the present application. And the same reference numbers appearing in the figures represent the same features or elements, as may be used in different embodiments.
The following describes the strategy and technical means of the antiwear method in detail by way of examples.
Example 1
The inlet anti-abrasion ring 1 of the impeller is provided with a drainage guide vane 4, and a working field diagram of the impeller assembly is shown in fig. 4 after the inlet anti-abrasion ring is provided with the drainage guide vane:
the scheme embodies the method strategy: the flow direction of fluid is changed at the inlet of the pump, vortex generation is prevented, mud mortar is divided in advance, direct opposite flushing with the head of the blade is avoided, the head of the blade (especially the upper half part of the blade with larger radius) is prevented from bearing the direct impact of the mud mortar, and therefore, the effect of protecting the head of the blade is achieved by designing the drainage guide vane on the inner wall of the inlet anti-abrasion ring of the impeller. The term "larger radius" as used in the art means: in the impeller blade, in order to distinguish different areas and parts of the same blade, the relative position relation is described or different positions are distinguished according to the radial size of the axial center of the part of the blade. This description is clear and normative.
Unlike the static guide vane installed inside the diffuser behind the impeller (or the diffuser and guide section of the multistage centrifugal pump), the guide vane 2 shown in figure 2 is installed on the inlet wear-resisting ring 1 of the impeller, a plurality of guide vanes 2 are uniformly distributed on the inner wall of the inlet wear-resisting ring 1 in the circumferential direction, and the guide vane 2 and the inlet wear-resisting ring 1 synchronously rotate along with the impeller; in addition, in the impeller, the number of the drainage guide vanes 2 is identical to that of the blades 4, and the arrangement positions of the drainage guide vanes are opposite to the blades 4, and gaps are reserved between the drainage guide vanes and the blades.
Therefore, the drainage guide vane 2 is not a traditional static guide vane, but a dynamic guide vane, the drainage guide vane 2 and the inlet anti-abrasion ring 1 synchronously rotate along with the impeller, the drainage guide vane 2 can change the flow direction of fluid under the non-rated working condition at the inlet of the impeller, not only can prevent vortex generation, but also can change the fluid trend to avoid direct impact on the head of the blade, and the embodiment shows that the problem of abrasion resistance of the head of the blade is fundamentally solved.
The drainage guide vane is positioned in front of the blade in the flow direction, and the technical means not only prevents the head of the blade from bearing direct forward under the rated working condition, but also prevents the head of the blade from bearing side forward direct forward under the non-rated working condition, so the embodiment also shows that the problem of abrasion resistance of the head of the blade is fundamentally solved.
In the form of the matching design, this embodiment is further innovated, and is shown in fig. 2 and 3: guide vane 2: the blade height (h) and the blade thickness (w) of the head part 2.1 to the tail part 2.2 are gradually increased, so that the flow dividing and guiding functions are enhanced, the flow blocking function (which can be controlled to be very small and almost negligible) is avoided, and the back flow and vortex generated by collision are avoided. The generation of the choked flow phenomenon is controlled, so that the generation of the vortex phenomenon is radically stopped. As to how to control the "no-flow effect" to be extremely small, the application task is disclosed by other patent applications, which further relates to the interrelationship model technical scheme of the leaf height (h), leaf thickness (w), application scene (spacing, position relation, size relation, etc.) of the head 2.1.
The technical scheme of the application is suitable for the impeller: the pump rotation shaft is located outside the impeller (shown in fig. 1, 2, and 3) and is not located inside the impeller.
The vanes 2 of the impeller are arranged and fixed on the inner wall of the inlet anti-abrasion ring 1, and the vanes are far away from the axis, so that the throughput of the pump is not affected.
The impeller blades 4 in the impeller and the guide vanes 2 are corresponding in number and position relation, the guide vanes 2 are in an 'axial and radial inward development' form, the tail parts (2.2) of the guide vanes are close to and opposite to the head parts (4.1) of the impeller blades (namely, the necessary technical characteristics of the application), the guide vanes mainly play roles in drainage, diversion and diversion, and the acting capacity is weak.
The traditional guide vane in the field is arranged behind the impeller and mainly plays roles of beam diffusion and radial force elimination. Those skilled in the art often avoid the use of conventional vanes in designing mud pumps to ensure throughput.
Therefore, the application is an innovation of the new functional application of the traditional guide vane.
Example 2
The slurry flow in the mud pump cannot be kept stable, and this instability also tends to occur near the impeller inlet, and the guide vane 2 and the vane 4 mounted on the inlet anti-wear ring 1 in example 1 are split into two bodies, so that a gap (at the vane front region B shown in fig. 6) is necessarily present, and the unstable pump flow may generate a vortex at the gap.
Therefore, the present embodiment 2 is based on the "guide vane" scenario disclosed in embodiment 1, and further discloses that the centrifugal mud pump is additionally provided with a high-pressure flushing technical means, and the "high-pressure flushing of the blade head" design is combined to enhance the application effect.
The obtained effect is as follows: the high-pressure flushing structure is positioned at the blade head (4.1) and the jet flow direction is reverse flow, and the purpose of the means is to form a reverse pressure gradient, so that the mud mortar is deviated in advance, and the blade head (4.1) is prevented from being impacted and worn. In the method, strategically, as the guide vanes (2) are arranged on the inlet anti-abrasion ring (1), the head parts (2.1) of the guide vanes are positioned in the inlet flow direction of the impeller, so that the parts with larger radius on the head parts (4.1) of the blades are similar in efficiency to continuously extend towards the inlet of the impeller, and each guide vane (2) is physically separated from the corresponding blade (4) in practice. On the one hand, the wear problem of the blade head (4.1) and the end face near the blade head (4.1) is directly and effectively solved, the weak point of the impeller blade is comprehensively protected, and therefore the durability of the mud pump is guaranteed. On the other hand, a drainage guide vane (2) is added at the inlet of the impeller, a matched high-pressure flushing structure is arranged at the head part (4.1) of the vane, and the combined scheme can further stabilize the running stability of the slurry and also improve the continuous abrasion of the slurry to the impeller.
The high-pressure flushing design of the application is different from other wall surface jet devices in principle, and belongs to a novel application of a structure in a mud pump based on a new principle.
The design of the high-pressure flushing of the blade head part is realized as follows:
the arrangement and location of the high pressure flush structure as shown in fig. 5 is schematically:
high-pressure water source and high-pressure sealing water between the impeller front cover plate (3) and the front pump cover and the lining plate (12) thereof are connected in the blades through a high-pressure flushing inlet pipe (13), a flushing hole/groove (6) is formed at the blade head (4.1), high-pressure flushing water is ejected from the blade head (4.1) through the flushing hole/groove (6), a reverse pressure gradient is formed in a clearance area (B in fig. 4 and 6) between the blades and the guide vane and is ejected along the guide vane tail (2.2), and the continuous water quality barrier weakens impact abrasion of vortex at the clearance to the blade head (4.1) on one hand and prevents vortex formation at the clearance on the other hand. The presence of the guide vane (2) together with the high-pressure flushing forms a continuous screen in the direction of the blade flow, protecting the blade head, in particular at the location of the blade head with a larger radius.
The nozzle is formed by arranging a flushing hole (groove) at the head of the blade.
The "direction of the incoming flow" is referred to as "countercurrent direction".
The high pressure flush of the vane head of example 2 alone is insufficient to create a sufficient counter pressure gradient to split the incoming slurry at small flush flows, while too large a flush flow may impede the incoming flow at certain inlet flow transients, destroy the suction performance of the mud pump, and even cause increased vane head wear due to the turbulence induced under abnormal conditions. In example 2, the cooperation of the high-pressure flushing water of the blade head and the drainage guide vane (2) further stably achieves the aim of reducing wear.
The combined application of the two structures in a forward direction of each other exemplifies:
1. if there is no drainage guide vane (2), the high pressure flushing can form a water barrier when facing the silt slurry in the forward direction or near the forward direction, so as to prevent the abrasion of the head part (4.1) of the blade, but when the silt pump runs under the obvious deviation from the common working condition, the flow direction of the silt slurry and the high pressure flushing can be in an obvious included angle, thereby generating strong vortex in the region (B) in front of the blade and affecting the antifriction effect. The flow guiding guide vane (2) not only shunts the inlet mud mortar, but also has the additional effect of optimizing the flow under the non-rated working condition, namely, under the pump operation working conditions of different concentration and granularity of mud mortar and different flow rates and rotating speeds, the flow guiding guide vane (2) guides the flow direction of the mud mortar impacting the blade head (4.1) into forward flow by a small amount of work, so that strong vortex is prevented from being generated in the front area (B) of the blade between the tail part (2.2) of the guide vane and the blade head (4.1), the suction performance of the impeller is ensured by the additional effect, and the effect of flushing the blade head is also improved;
2. the drainage guide vane (2) also has the function of guaranteeing the flushing action range: the existence of the guide vane prevents the slurry from directly punching the vane, so that the pressure difference in the gap (B area) between the vane and the guide vane is reduced, and the tail part (2.2) of the guide vane is easier to be impacted by high-pressure flushing; and the diversion effect of the guide vane tail part (2.2) on flushing water also prevents the overlarge action range of flushing water. Therefore, the two structures are combined to increase the adaptability of the high-pressure flushing water quantity, and even if the high-pressure water of the blade head (4.1) changes in a wider flow range, the water barrier can be ensured to be full and restrained in the gap (B area) between the guide blade tail (2.2) and the blade head (4.1). For unstable inflow mud mortar, no matter the flushing flow is relatively smaller or larger, the effect of 'preventing the mud mortar from generating vortex in the gap' is exerted, and the improvement of the abrasion of the blade head is ensured.
Claims (4)
1. The antiwear method applied to the centrifugal mud pump is characterized by comprising the following steps of:
a drainage guide vane is designed on an inlet anti-abrasion ring of the impeller, and a strategy of dividing the mud mortar in advance is adopted to deviate and guide the mud mortar, so that the head of the impeller is prevented from bearing the direct impact of the mud mortar; the guide vanes (2) are arranged on an inlet anti-wear ring (1) of the impeller, the guide vanes (2) are uniformly distributed on the inner wall of the inlet anti-wear ring (1) in the circumferential direction, and the guide vanes (2) and the inlet anti-wear ring (1) synchronously rotate along with the impeller;
meanwhile, the drainage guide vane (2) on the inlet anti-wear ring (1) and the corresponding vane (4) are divided into two bodies, and a spacing area B exists;
meanwhile, a high-pressure flushing structure is designed on the blade (4), the high-pressure flushing structure is matched with the drainage guide vane (2), the high-pressure flushing forms countercurrent jet flow from the blade head (4.1), and a reverse pressure gradient is formed to enable the mud mortar to deviate in advance, so that the formation of a mud mortar vortex in the interval area B is avoided, and finally, the impact of mud on the worn blade head (4.1) is avoided.
2. A method according to claim 1, characterized in that in the impeller the number of guide vanes (2) corresponds to the number of blades (4), which are arranged opposite the blades (4), leaving a gap between them.
3. The method according to claim 1, characterized in that the guide vane (2) is close to and facing the head of the impeller blade (4).
4. A method according to claim 1, characterized in that the high-pressure water source and the high-pressure sealing water between the impeller front cover plate (3) and the front pump cover and the lining plate (12) thereof are connected in the blade (4) through a high-pressure flushing inlet pipe (13), the surface of the blade head (4.1) is provided with a flushing hole/groove (6), the high-pressure flushing water is injected from the surface of the blade head (4.1) through the flushing hole/groove (6) in an incident flow manner, a reverse pressure gradient is formed in a clearance area between the blade (4) and the drainage guide vane (2), and the high-pressure flushing water is injected along the tail part (2.2) of the guide vane.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110511864.XA CN114076103B (en) | 2021-05-11 | 2021-05-11 | Wear-resistant design method for centrifugal mud pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110511864.XA CN114076103B (en) | 2021-05-11 | 2021-05-11 | Wear-resistant design method for centrifugal mud pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114076103A CN114076103A (en) | 2022-02-22 |
| CN114076103B true CN114076103B (en) | 2023-11-17 |
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| CN202110511864.XA Active CN114076103B (en) | 2021-05-11 | 2021-05-11 | Wear-resistant design method for centrifugal mud pump |
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1445356A (en) * | 1972-12-28 | 1976-08-11 | Leipzig Chemieanlagen | Centrifugal pump |
| CN201339613Y (en) * | 2009-01-15 | 2009-11-04 | 江苏耐尔冶电集团有限公司 | Mud pump with water flushing device |
| CN106678082A (en) * | 2017-01-24 | 2017-05-17 | 浙江工业大学 | Mechanism for inhibiting backflow vortex of impeller inlet of centrifugal pump |
| CN107956737A (en) * | 2017-12-16 | 2018-04-24 | 山东双轮股份有限公司 | Low net positive suction head low-pressure fluctuation centrifugal pump |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10746196B2 (en) * | 2017-04-09 | 2020-08-18 | Technology Commercialization Corp. | Methods and devices for reducing circumferential pressure imbalances in an impeller side cavity of rotary machines |
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Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1445356A (en) * | 1972-12-28 | 1976-08-11 | Leipzig Chemieanlagen | Centrifugal pump |
| CN201339613Y (en) * | 2009-01-15 | 2009-11-04 | 江苏耐尔冶电集团有限公司 | Mud pump with water flushing device |
| CN106678082A (en) * | 2017-01-24 | 2017-05-17 | 浙江工业大学 | Mechanism for inhibiting backflow vortex of impeller inlet of centrifugal pump |
| CN107956737A (en) * | 2017-12-16 | 2018-04-24 | 山东双轮股份有限公司 | Low net positive suction head low-pressure fluctuation centrifugal pump |
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| CN114076103A (en) | 2022-02-22 |
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