Large-flow abrasion-resistant sectional volute multistage pump

Abstract

The utility model relates to a large-flow abrasion-resistant sectional volute multi-stage pump. The multi-stage pump comprises a driving end bearing component, a rotor component, a sealing component, a first auxiliary impeller, a suction section, a volute body, a sealing ring, a connecting component, an impeller, a discharge section, a final-stage impeller, a balance drum, a second auxiliary impeller, a balance pipe, a pump shaft and a free end bearing component. The original radial guide vane and the annular middle section are combined, so that the water pump is more compact in structure and convenient and reliable to process and cast. And the inner side of the impeller cover plate is designed to be gradually expanded, so that the scouring of particles in a medium to a pump body runner and the impeller cover plate is effectively reduced. Due to the design of the sealing ring of the pump body and the multi-line reverse thread groove of the impeller, the throttling effect is effectively improved, and the operation efficiency of the pump is improved. The front portions of the sealing cavities at the two ends are each provided with a set of auxiliary impeller device, non-contact sealing is provided for the pump, and silt or other solid particles are effectively prevented from entering the sealing device of the pump.

Description

Technical Field

[0001] This utility model relates to a segmental volute multistage pump, specifically a high-flow-rate, wear-resistant segmental volute multistage pump with a compact structure, convenient and reliable processing and casting, good resistance to erosion and abrasion, low manufacturing cost, and long service life of each component. Background Technology

[0002] High-flow, wear-resistant, segmental volute multistage pumps are widely used fluid transport equipment in industrial fields. Their working principle primarily relies on the cascade action of multiple impellers to achieve fluid pressurization and transport. This design not only improves the pump's head capacity but also makes flow control more stable and reliable. Structurally, multistage pumps typically consist of a stator, rotor, balancing mechanism, and bearings. The rotor is the core component, consisting of a shaft and multiple impellers, while the stator includes inlet and outlet sections and an intermediate guide vane housing.

[0003] When a multistage pump is in operation, if the process medium contains a large amount of silt or other solid particles, the hard silt or solid particles will cause severe wear and damage to the surfaces of the flow components, water guide bearings, and sealing components. Severe wear of pump components will have serious consequences, ranging from requiring frequent repairs and maintenance and replacement of the pump set to serious operational events such as seizure and jamming, resulting in huge economic losses. Utility Model Content

[0004] To address the aforementioned problems, the main objective of this utility model is to provide a high-flow, wear-resistant, segmental volute multistage pump with a compact structure, convenient and reliable processing and casting, good resistance to erosion and abrasion, low manufacturing cost, and long service life of each component.

[0005] This utility model solves the above-mentioned technical problems through the following technical solution: a high-flow-rate, wear-resistant, segmental volute multistage pump, the high-flow-rate, wear-resistant, segmental volute multistage pump comprising: a drive end bearing assembly, a rotor assembly, a sealing assembly, a first auxiliary impeller, a suction section, a volute casing, a sealing ring, a connecting assembly, an impeller, a discharge section, a final stage impeller, a balance drum, a second auxiliary impeller, a balance pipe, a pump shaft, and a free end bearing assembly.

[0006] The drive end bearing assembly and the free end bearing assembly are located at the drive end and the free end of the multistage pump, respectively. The suction section and the discharge section are located at the inlet and outlet of the multistage pump, respectively. Between the suction section and the discharge section are several impellers and the final stage impeller. The front part of the sealing component cavity at the drive end is designed with a first set of impellers, and the front part of the sealing component cavity at the free end is designed with a second set of impellers.

[0007] The rotor assembly includes a first impeller, several impellers, a final stage impeller, a balance drum, a pump shaft, a drive end bearing assembly, a second impeller, and a free end bearing assembly; the pump shaft is connected to a motor; the first impeller, several impellers, the final stage impeller, the balance drum, and the second impeller are all fixed on the pump shaft.

[0008] The volute housing is a symmetrical volute housing, which is a combination of radial guide vanes and an annular middle section. The connecting component is installed between the intake section and the discharge section, with both ends distributed and fixed on the intake section and the discharge section.

[0009] The balancing drum is located between the final impeller and the second auxiliary impeller; a balancing chamber is provided between the discharge section and the free end, and the balancing chamber is connected to the suction section through a balancing pipe. The balancing drum and the balancing chamber together form the axial force balancing device of the pump unit.

[0010] In a specific embodiment of this utility model, the inhalation section and the discharge section each have pre-drilled mounting holes for connecting components. The connecting components have threads at both ends and are fixed with nuts.

[0011] In a specific embodiment of this utility model, there are four volute housings, which are symmetrically distributed around the circumference.

[0012] In a specific embodiment of this utility model, the end face of the volute housing adopts a spiral protrusion structure.

[0013] In a specific embodiment of this utility model, the inner side of the cover plate of both the impeller and the final stage impeller adopts a gradually expanding design.

[0014] In a specific embodiment of this utility model, both the sealing ring and the impeller mating circumferential surface are designed with multi-threaded grooves, and the multi-threaded grooves of the two are rotated in opposite directions.

[0015] In a specific embodiment of this utility model, a rectangular groove is designed at the inlet end of the impeller, and its spiral direction is opposite to the rotation direction of the impeller and the last stage impeller.

[0016] In a specific embodiment of this utility model, the drive-side intake section is designed with a return flow hole.

[0017] In a specific embodiment of this utility model, the ejection section is an ejection section with a volute-type hydraulic design.

[0018] In a specific embodiment of this utility model, the rear cover plate of the final stage impeller is designed with helical secondary blades.

[0019] The positive and progressive effects of this utility model are as follows: Compared with common technologies, the high-flow wear-resistant segmental volute multistage pump provided by this utility model has the following advantages: This utility model adopts a high-efficiency, compact, and symmetrical volute design, which combines the original radial guide vanes and annular middle section, making the pump structure more compact, easy and reliable to process and cast, with good erosion resistance and significantly improved pump operating efficiency.

[0020] The impeller cover plate of this utility model adopts a gradually expanding design on the inner side, and the pump body volute end face adopts a spiral and protruding structure. When used in conjunction with the impeller, it effectively reduces the scouring of the pump body flow channel and impeller cover plate by the particles inside the medium.

[0021] The sealing ring and impeller inlet sealing ring of this utility model adopt a multi-line reverse thread groove design, which effectively improves the throttling effect and increases the pump operating efficiency while ensuring the operating clearance.

[0022] This utility model features a rectangular groove at the impeller inlet end, which solves the problem of solid particles and impurities accumulating at the impeller inlet and prevents solid particles and impurities from entering the dynamic and static gap of the sealing ring. This reduces the erosion of the sealing ring and impeller by impurities and improves operational reliability.

[0023] This utility model features a secondary impeller designed before the sealing cavity. While providing a non-contact seal to the pump, the secondary impeller effectively prevents mud, sand, or other solid particles from entering the pump's sealing device, thus preventing wear and damage to the sealing components. This improves the service life and reliability of the sealing components, thereby enhancing the user's economic benefits.

[0024] The present invention has a reflux hole at the suction end. Under the action of centrifugal force of the auxiliary impeller, solid particles and impurities enter the suction port through the reflux hole, thereby effectively solving the problem of solid particles and impurities accumulating in the sealing cavity and suction port, inhibiting the scouring of the sealing components and flow components by solid particles and impurities, and improving the wear and corrosion resistance of the pump unit.

[0025] The discharge section of this utility model adopts a volute hydraulic design, eliminating radial guide vanes. While reducing the number of pump components, it improves the pump's resistance to wear and erosion, resulting in a significant increase in pump operating efficiency. Furthermore, its structure is more compact than that of radial guide vanes, and its processing and casting are more convenient and reliable. Attached Figure Description

[0026] Figure 1 This is a schematic diagram of the overall structure of this utility model.

[0027] Figure 2-1 This is a schematic diagram of the secondary impeller in this utility model.

[0028] Figure 2-2 for Figure 2-1 AA view.

[0029] Figure 2-3 for Figure 2-1 BB view.

[0030] Figure 3-1 This is a schematic diagram of the impeller structure in this utility model.

[0031] Figure 3-2 for Figure 3-1 The left view.

[0032] Figure 3-3 for Figure 3-1 The right view.

[0033] Figure 4 This is a schematic diagram of the volute housing in this utility model.

[0034] The following are the names corresponding to the reference numerals in this utility model:

[0035] Drive end bearing component 1, rotor component 2, sealing component 3, first auxiliary impeller 4, suction section 5, volute casing 6, sealing ring 7, connecting component 8, impeller 9, discharge section 10, final stage impeller 11, balance drum 12, second auxiliary impeller 13, balance pipe 14, pump shaft 15, free end bearing component 16, return hole 17, spiral protrusion structure 601, multi-threaded groove 901, rectangular groove 902, spiral auxiliary blade 1101. Detailed Implementation

[0036] The preferred embodiments of this utility model are given below with reference to the accompanying drawings to illustrate the technical solution of this utility model in detail.

[0037] Figure 1 This is a schematic diagram of the overall structure of the present invention, as shown below. Figure 1 As shown, this utility model proposes a high-flow-rate, wear-resistant, segmental volute multistage pump, which includes: a drive-end bearing assembly 1, a rotor assembly 2, a sealing assembly 3, a first auxiliary impeller 4, a suction section 5, a volute casing 6, a sealing ring 7, a connecting assembly 8, an impeller 9, a discharge section 10, a final stage impeller 11, a balance drum 12, a second auxiliary impeller 13, a balance pipe 14, a pump shaft 15, and a free-end bearing assembly 16.

[0038] The drive-end bearing assembly 1 and the free-end bearing assembly 16 are located at the drive end and free end of the multistage pump, respectively. The suction section 5 and the discharge section 10 are located at the inlet and outlet of the multistage pump, respectively. Between the suction section 5 and the discharge section 10 are several impellers 9 and a final stage impeller 11. The front part of the sealing component 3 at the drive end is designed with a first auxiliary impeller 4, and the front part of the sealing component 3 at the free end is designed with a second auxiliary impeller 13 (the first auxiliary impeller 4 and the second auxiliary impeller 13 have the same structure, see [reference]). Figure 2-1 , 2-2 2-3).

[0039] The rotor assembly 2 includes a first impeller 4, several impellers 9, a final stage impeller 11, a balance drum 12, a pump shaft 15, a drive end bearing assembly 1, a second impeller 13, and a free end bearing assembly 16; the pump shaft 15 is connected to a motor; the first impeller 4, several impellers 9, the final stage impeller 11, the balance drum 12, and the second impeller 13 are all fixed on the pump shaft 15.

[0040] The volute casing 6 is a symmetrical volute casing, which is a combination of radial guide vanes and an annular middle section. The connecting component 8 is installed between the suction section and the discharge section, with both ends fixed to the suction section and the discharge section. For segmented pumps, each stage needs to be pressed tightly at the outermost edge, and the connecting component is used to press the whole structure together. In the actual implementation, the suction section and the discharge section each have pre-drilled mounting holes for the connecting component 8. The connecting component has threads at both ends, which are fixed with nuts.

[0041] The balancing drum 12 is located between the final impeller 11 and the second impeller 13; a balancing chamber is provided between the discharge section 10 and the free end, and the balancing chamber is connected to the suction section 5 through the balancing pipe 14. The balancing drum 12 and the balancing chamber together form the axial force balancing device of the pump group.

[0042] In the specific implementation process, there are four volute housings 6, which are symmetrically distributed around the circumference. The volute housing 6 combines the original radial guide vanes and annular middle section design, which serves as both the flow channel and the pressure-bearing component of the pump unit. The design of the volute housing 6 reduces the axial dimension of the water pump, making the water pump structure more compact. Compared with the radial guide vanes, it is easier and more reliable to process and cast. Moreover, its flow channel shape is more in line with the liquid flow characteristics, making the volute housing 6 more resistant to erosion and abrasion, and the water pump operates more efficiently and reliably.

[0043] Figure 3-1 This is a schematic diagram of the impeller structure in this utility model. Figure 3-2 for Figure 3-1 Left view, Figure 3-3 for Figure 3-1 The right view. As shown in the figure above: In the specific implementation process, the inner side of the cover plate of impeller 9 and the last stage impeller 11 adopts a gradually expanding design, see [reference]. Figure 3-1 At point A in the diagram, the end face of the volute housing 6 adopts a helical protrusion structure 601, see [reference]. Figure 4 Solid particles and impurities are pressurized by impeller 9 and the last stage impeller 11 and moved to the gradually expanding outlet of impeller 9 and the last stage impeller 11. Then they enter the volute and are discharged after being centrifugally discharged by the spiral protrusion end face of the volute casing 6. This effectively solves the problem of solid particles and impurities being retained and scourted by the volute casing 6. The design of the volute casing 6 in conjunction with impeller 9 and the last stage impeller 11 effectively reduces the scour of the pump body flow channel and impeller cover plate by particles inside the medium.

[0044] In the specific implementation process, both the sealing ring 7 and the impeller 9 are designed with multi-threaded grooves 901 on their mating circumferential surfaces. The multi-threaded grooves rotate in opposite directions. During operation, the two multi-threads interact to generate a reverse spiral sealing effect, preventing the fluid leaking from the volute 6 from flowing back to the inlet of the impeller 9. Furthermore, due to the propulsive action of the reverse multi-threads, solid particles and impurities are effectively prevented from entering between the sealing ring 7 and the impeller 9. While ensuring the operating clearance, the throttling effect is effectively improved, enhancing the pump's operating efficiency and safety.

[0045] In the specific implementation process, the inlet end of the impeller 9 is designed with a rectangular groove 902, the spiral direction of which is opposite to the rotation direction of the impeller 9 and the last stage impeller 11. When the pump unit is running, solid particles and impurities at the impeller inlet enter the impeller 9 inlet under the action of centrifugal force, which effectively solves the problem of solid particles and impurities accumulating at the inlet of the double suction impeller 9, prevents solid particles and impurities from entering between the sealing ring 7 and the impeller 9, reduces the scouring of the sealing ring 7 and the impeller 9 by impurities, and improves the reliability of operation.

[0046] In the specific implementation process, the front part of the cavity of the drive end and free end sealing component 3 is designed with a first impeller 4. The first impeller 4 provides a non-contact seal for the pump and also effectively prevents mud or other solid particles from entering the pump's sealing components, effectively protecting the sealing device, extending the service life of the sealing components, improving the safe operation cycle of the pump set, and thus generating higher economic benefits.

[0047] In the specific implementation process, the drive-side suction section 5 is designed with a return port 17. Under the centrifugal force of the first impeller 4, solid particles and impurities enter the suction port through the return port. The discharge section 10 is designed with a balancing chamber. The balancing drum 12 and the balancing chamber together form the axial force balancing device of the pump unit. Compared with the existing balancing disc design, it is simple to manufacture and reliable in operation. The balancing chamber is connected to the suction section 5 through a balancing pipe 14. While balancing the axial force, it also allows solid particles and impurities to return to the suction port under the centrifugal force of the second impeller 13. This effectively solves the problem of solid particles and impurities accumulating in the sealing chamber and suction port, improves the pump unit's erosion resistance, and enhances the pump unit's operational reliability.

[0048] In the specific implementation process, the discharge section 10 adopts a volute hydraulic design, eliminating the radial guide vanes. The volute hydraulic design is more in line with the liquid flow state, thus making the volute casing more resistant to wear and erosion, significantly improving the pump's operating efficiency. Furthermore, its structure is more compact than that of radial guide vanes, and its machining and casting are more convenient and reliable. Additionally, the rear cover plate of the final stage impeller 11 is designed with helical auxiliary blades 1101. While balancing the axial force, the centrifugal effect of the auxiliary blades effectively inhibits solid particles and impurities from entering the gap between the balancing drum 12 and the balancing chamber, improving the erosion resistance of the balancing device and enhancing the operational reliability of the pump unit.

[0049] This utility model adopts a high-efficiency, compact, symmetrical volute design, which combines the original radial guide vanes and annular middle section, making the pump structure more compact, easy and reliable to process and cast, with good resistance to erosion and abrasion, and significantly improving the pump's operating efficiency.

[0050] The impeller cover plate of this utility model adopts a gradually expanding design on the inner side, and the pump body volute end face adopts a spiral and protruding structure. When used in conjunction with the impeller, it effectively reduces the scouring of the pump body flow channel and impeller cover plate by the particles inside the medium.

[0051] The sealing ring and impeller inlet sealing ring of this utility model adopt a multi-line reverse thread groove design, which effectively improves the throttling effect and increases the pump operating efficiency while ensuring the operating clearance.

[0052] This utility model features a rectangular groove at the impeller inlet end, which solves the problem of solid particles and impurities accumulating at the impeller inlet and prevents solid particles and impurities from entering the dynamic and static gap of the sealing ring. This reduces the erosion of the sealing ring and impeller by impurities and improves operational reliability.

[0053] This utility model features a secondary impeller designed before the sealing cavity. While providing a non-contact seal to the pump, the secondary impeller effectively prevents mud, sand, or other solid particles from entering the pump's sealing device, thus preventing wear and damage to the sealing components. This improves the service life and reliability of the sealing components, thereby enhancing the user's economic benefits.

[0054] The present invention has a reflux hole at the suction end. Under the action of centrifugal force of the auxiliary impeller, solid particles and impurities enter the suction port through the reflux hole, thereby effectively solving the problem of solid particles and impurities accumulating in the sealing cavity and suction port, inhibiting the scouring of the sealing components and flow components by solid particles and impurities, and improving the wear and corrosion resistance of the pump unit.

[0055] The discharge section of this utility model adopts a volute hydraulic design, eliminating radial guide vanes. While reducing the number of pump components, it improves the pump's resistance to wear and erosion, resulting in a significant increase in pump operating efficiency. Furthermore, its structure is more compact than that of radial guide vanes, and its processing and casting are more convenient and reliable.

[0056] The foregoing has shown and described the basic principles, main features, and advantages of this utility model. Those skilled in the art should understand that this utility model is not limited to the above embodiments. The embodiments and descriptions in the specification are merely illustrative of the principles of this utility model. Various changes and modifications can be made to this utility model without departing from its spirit and scope, and all such changes and modifications fall within the scope of protection of this utility model as defined by the appended claims and their equivalents.

Claims

1. A high-flow-rate, wear-resistant, segmental volute multistage pump, characterized in that: The high-flow, wear-resistant, corrosion-resistant segmental volute multistage pump includes: Drive end bearing assembly, rotor assembly, sealing assembly, first auxiliary impeller, suction section, volute casing, sealing ring, connecting assembly, impeller, discharge section, final stage impeller, balance drum, second auxiliary impeller, balance pipe, pump shaft, free end bearing assembly; The drive end bearing assembly and the free end bearing assembly are located at the drive end and the free end of the multistage pump, respectively. The suction section and the discharge section are located at the inlet and outlet of the multistage pump, respectively. Between the suction section and the discharge section are several impellers and the final stage impeller. The front part of the sealing component cavity at the drive end is designed with a first set of impellers, and the front part of the sealing component cavity at the free end is designed with a second set of impellers. The rotor assembly includes a first impeller, several impellers, a final stage impeller, a balance drum, a pump shaft, a drive end bearing assembly, a second impeller, and a free end bearing assembly; the pump shaft is connected to a motor; the first impeller, several impellers, the final stage impeller, the balance drum, and the second impeller are all fixed on the pump shaft; The volute is a symmetrical volute, which is a combination of radial guide vanes and an annular middle section. The connecting parts are installed between the intake section and the discharge section, and the two ends are distributed and fixed on the intake section and the discharge section. The balancing drum is located between the final impeller and the second auxiliary impeller; a balancing chamber is provided between the discharge section and the free end, and the balancing chamber is connected to the suction section through a balancing pipe. The balancing drum and the balancing chamber together form the axial force balancing device of the pump unit.

2. The high-flow-rate, wear-resistant, segmental volute multistage pump according to claim 1, characterized in that: The suction section and the discharge section each have pre-drilled mounting holes for connecting components. The connecting components have threads at both ends and are secured with nuts.

3. The high-flow-rate, wear-resistant, segmental volute multistage pump according to claim 1, characterized in that: There are four volutes, and they are symmetrically distributed around the circumference.

4. The high-flow-rate, wear-resistant, segmental volute multistage pump according to claim 1, characterized in that: The end face of the volute housing adopts a spiral protrusion structure.

5. The high-flow-rate, wear-resistant, segmental volute multistage pump according to claim 1, characterized in that: The inner side of the cover plates of both the impeller and the final stage impeller adopts a gradually expanding design.

6. The high-flow-rate, wear-resistant, segmental volute multistage pump according to claim 1, characterized in that: Both the sealing ring and the impeller mating circumferential surface are designed with multi-threaded grooves, and the multi-threaded grooves of the two are rotated in opposite directions.

7. The high-flow-rate, wear-resistant, segmental volute multistage pump according to claim 1, characterized in that: The impeller inlet end is designed with a rectangular groove, the spiral direction of which is opposite to the rotation direction of the impeller and the last stage impeller.

8. The high-flow-rate, wear-resistant, segmental volute multistage pump according to claim 1, characterized in that: The drive-side intake section is designed with a reflux hole.

9. The high-flow-rate, wear-resistant, segmental volute multistage pump according to claim 1, characterized in that: The discharge section is designed with a spiral hydraulic system.

10. The high-flow-rate, wear-resistant, segmental volute multistage pump according to claim 1, characterized in that: The rear cover plate of the final stage impeller is designed with helical secondary blades.

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