CN114857035B - Sealing structure for centrifugal pump - Google Patents
Sealing structure for centrifugal pump Download PDFInfo
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- CN114857035B CN114857035B CN202110171359.5A CN202110171359A CN114857035B CN 114857035 B CN114857035 B CN 114857035B CN 202110171359 A CN202110171359 A CN 202110171359A CN 114857035 B CN114857035 B CN 114857035B
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- impeller
- pump
- sealing structure
- central
- seat
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- 238000007789 sealing Methods 0.000 title claims abstract description 33
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 67
- 230000003068 static effect Effects 0.000 claims abstract description 8
- 230000002093 peripheral effect Effects 0.000 claims description 11
- 239000012535 impurity Substances 0.000 claims description 4
- 229910000831 Steel Inorganic materials 0.000 claims description 3
- 238000004891 communication Methods 0.000 claims description 3
- 239000012530 fluid Substances 0.000 claims description 3
- 238000000034 method Methods 0.000 claims description 3
- WFKWXMTUELFFGS-UHFFFAOYSA-N tungsten Chemical compound [W] WFKWXMTUELFFGS-UHFFFAOYSA-N 0.000 claims description 3
- 229910052721 tungsten Inorganic materials 0.000 claims description 3
- 239000010937 tungsten Substances 0.000 claims description 3
- 239000010959 steel Substances 0.000 claims description 2
- 239000000411 inducer Substances 0.000 description 11
- 239000011248 coating agent Substances 0.000 description 4
- 238000000576 coating method Methods 0.000 description 4
- 239000000463 material Substances 0.000 description 2
- 238000004381 surface treatment Methods 0.000 description 2
- 239000003831 antifriction material Substances 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000003090 exacerbative effect Effects 0.000 description 1
- 230000002262 irrigation Effects 0.000 description 1
- 238000003973 irrigation Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 239000013049 sediment Substances 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- 238000003466 welding Methods 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
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
- F04D13/08—Units comprising pumps and their driving means the pump being electrically driven for submerged use
- F04D13/10—Units comprising pumps and their driving means the pump being electrically driven for submerged use adapted for use in mining bore holes
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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
- F04D29/08—Sealings
- F04D29/086—Sealings 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
- F04D29/40—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)
- Mining & Mineral Resources (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
A sealing structure for a centrifugal pump, the centrifugal pump comprising: motor assembly, pump shaft and pump body subassembly. The pump body assembly includes a pump sleeve and a plurality of impeller stage sets. The impeller stage group comprises a support shell, a flow guiding shell and an impeller. The impeller includes a hub, a tapered wall, blades, and an impeller seat. The sealing structure comprises a dynamic sealing structure and a water throwing groove sealing structure. The dynamic seal structure includes an outer static seal ring. The outer stationary seal ring includes a radial contact and an axial contact. The radial contact portion and the cylindrical base portion of the impeller seat of the impeller of the centrifugal pump define a first space therebetween, and the axial contact portion and the cylindrical base portion define a second space therebetween. The width of the first space in the radial direction is smaller than the width of the second space in the axial direction. The water throwing groove sealing structure comprises a plurality of water throwing grooves which are arranged along the circumference of the diversion shell.
Description
Technical Field
The application relates to a sealing structure for a centrifugal pump, in particular to a sealing structure for a multistage centrifugal pump for a deep well with high rotation speed and high lift.
Background
Centrifugal pumps for deep wells generally include a motor assembly and a pump body assembly including an impeller driven to rotate by a pump shaft. The pump shaft rotation speed of the traditional centrifugal pump is generally about 3000rpm, and if the lift of the water output by the centrifugal pump reaches 300m, the height of the centrifugal pump can reach 3m, so the deep-well pump is large and heavy.
Centrifugal pumps for deep wells are mostly used for agricultural irrigation, and the use environment is usually at a depth of 100-500 m in the well. In applications where the natural environment is severe, such as mountain, the operation is very inconvenient. In particular, only for the handling of centrifugal pumps, the personnel have to lift to the mountain top, which can take hours or even days, and it is very difficult to install large, heavy centrifugal pumps down the bottom of a well, which can be hundreds of meters deep, and possibly for subsequent maintenance. This limits the application of centrifugal pumps to a large extent. In the process of improving the pump, in order to increase the lift of the centrifugal pump, means for increasing the diameter of the impeller are generally adopted, which further increases the volume and weight of the pump, exacerbating the above-mentioned inconvenience of the pump.
In such a case, the sealing structure in the centrifugal pump consumes a great deal of work and generates vibration, thereby reducing the overall efficiency of the centrifugal pump.
Disclosure of Invention
The application aims to provide a water throwing groove sealing structure for a centrifugal pump, which reduces water flow leakage and simultaneously reduces friction resistance and vibration of an impeller stage group.
To this end, the application proposes a sealing structure for a centrifugal pump comprising: the pump comprises a motor assembly providing rotational movement, a pump shaft driven by an output shaft of the motor assembly, and a pump body assembly, wherein the pump body assembly comprises a pump sleeve and a plurality of impeller stage groups accommodated in the pump sleeve, and the impeller stage groups comprise: a support housing and a guide housing attached together in an axial direction to define an impeller cavity, and an impeller housed within the impeller cavity to be driven by a pump shaft to rotate synchronously therewith, wherein the impeller comprises: a hub defining a central bore for engagement with a pump shaft, and a conical wall extending radially outwardly and axially upwardly from the hub, a vane extending helically from a lower surface of the conical wall, and an impeller seat attached to an outer periphery of the vane, the impeller seat defining an outer support end surface at a lower end thereof, characterized in that the sealing structure comprises a dynamic sealing structure comprising an outer static sealing ring comprising a radial contact portion parallel to the axial direction and an axial contact portion perpendicular to the axial direction, wherein the radial contact portion defines a first space with a cylindrical base of the impeller seat of an impeller of the centrifugal pump, and a second space between the axial contact portion and the cylindrical base, wherein a width of the first space in the radial direction is smaller than a width of the second space in the axial direction, the impeller seat defining a plurality of flighting grooves disposed radially outwardly of the outer support end surface at a lower end of the impeller seat, wherein the plurality of flighting grooves are arranged along a circumferential direction of the flow guiding housing.
According to an alternative embodiment, each of the plurality of water slingers comprises two sides arranged at an angle, the angle between the two sides being between 50 ° and 70 °.
According to an alternative embodiment, the flow guiding housing of the impeller stage group comprises a central portion having a central hole allowing the pump shaft to extend through, a peripheral portion axially engaged with the support housing and guide vanes extending helically between the central portion and the peripheral portion, the central portion, the peripheral portion and the guide vanes defining the flow guiding channel of the impeller stage group.
According to an alternative embodiment, the impeller seat, the conical wall and the blades define a centrifugal channel, the hub defines a central support end surface perpendicular to the axial direction, the central support end surface is defined by the hub of the impeller or a central movable sealing ring embedded in the lower end of the hub, the flow guiding housing comprises a central abutment end surface in constant abutting contact with the central support end surface, and the flow guiding channel is in fluid communication with the centrifugal channel.
According to an alternative embodiment, the centering seal ring is constructed of tungsten steel.
According to an alternative embodiment, the central portion is a deflector seat formed separately and attached to the peripheral portion.
According to an alternative embodiment, the central abutment end surface is provided by a deflector seat or a central static sealing ring embedded in the deflector seat.
According to an alternative embodiment, the hub portion extends beyond the support housing at a first axial end in an axial direction away from the motor assembly, and terminates at a central abutment end surface within the support housing at a second axial end opposite the first axial end.
According to an alternative embodiment, the impeller seat and the support housing define an annular gap.
According to an alternative embodiment, the support housing, the deflector housing and the impeller seat together define a dirt collection space for receiving dirt from the annular gap.
According to the water throwing groove sealing structure for the centrifugal pump, in the running state of the centrifugal pump, due to the action of upward flowing water and centrifugal force of the impeller, the external static sealing ring is not contacted with the cylindrical base part of the impeller seat of the impeller of the centrifugal pump, a gap is formed, and the friction power consumption of the impeller is reduced. Meanwhile, the water in the second space is thrown out under the centrifugal force, thereby forming an internal water pressure against the external water pressure, so that the impeller can reduce the radial force generated by the water. In addition, the water pressure balance also enables the impeller and the diversion shell to be always sealed, and the sealing failure caused by the high-speed rotation of the impeller can be avoided. In the high-speed running state of the centrifugal pump, the water is thrown out by the water throwing tanks to form kinetic energy, and the kinetic energy is opposed to external water pressure so as to reduce water flow leakage, and meanwhile, the impeller is enabled to reach a dynamic floating state in the high-speed running state of the centrifugal pump so as to reduce friction resistance and vibration of the impeller stage group.
Drawings
The foregoing and other features, advantages and benefits of the application will be described in detail below with reference to the following drawings in conjunction with exemplary embodiments of the application. It should be understood that the drawings are not to scale and are intended to illustrate the principles of the application and not to limit the application to the illustrated embodiments.
FIG. 1 is a longitudinal cross-sectional view of an exemplary centrifugal pump of the present application;
fig. 2 shows a longitudinal section through an impeller stage set of the centrifugal pump of fig. 1;
Fig. 3 shows a perspective view of an impeller of the impeller stage group of fig. 2; and
Fig. 4 shows an enlarged perspective view of section a of the impeller of fig. 3.
Detailed Description
The centrifugal pump of the present application is described in detail below with reference to the accompanying drawings. The same reference numbers will be used throughout the drawings to refer to the same or like parts in structure or function.
Fig. 1 is a longitudinal section of an exemplary centrifugal pump of the present application. In general, centrifugal pumps include a motor assembly and a pump body assembly 20. The motor assembly includes a motor housing and a motor, such as an electric motor, housed within the motor housing capable of outputting a high rotational speed. An auxiliary system, such as a cooling system, that provides auxiliary functions for the operation of the motor is also provided within the motor housing. The pump body assembly 20 includes a pump sleeve 22 and a plurality of impeller stage sets 200 housed within the pump sleeve 22. The output shaft of the motor drives the rotation of the impeller 70 of each impeller stage group 200 in the centrifugal pump through the pump shaft 11 of the centrifugal pump. In the illustrated embodiment, the pump shaft 11 is a six-tooth pump shaft.
In the present application, for convenience of description, the direction in which the pump shaft 11 extends is defined as an axial direction, and a circumferential direction extends around the axial direction. The centrifugal pump of the application is usually placed vertically during use, so the axial direction is also referred to as vertical direction, the direction/end towards the motor assembly in the axial direction is referred to as lower/lower end, and the opposite direction/end is referred to as upper/upper end. In a plane perpendicular to the axial direction, a direction from the pump sleeve 22 toward the central axis of the pump shaft 11 is referred to as radially inward, and a direction from the central axis of the pump shaft 11 toward the pump sleeve 22 is referred to as radially outward, with reference to the central axis of the pump shaft 11 defining the axial direction.
Referring back to fig. 1, in the axial direction, the pump body assembly 20 sequentially includes, from bottom to top, a water intake section 30, an impeller section 50 composed of a plurality of impeller stage groups, and a water discharge section 40, the structure of each section being described in detail below.
In the water intake section 30, water intake holes 32 distributed in the circumferential direction are provided on the pump sleeve 22, and in the water intake section 30, a cone housing 34 is provided inside the pump sleeve 22. The cone housing 34 is configured as an inverted cone opening to the motor assembly, including a central bore that allows the pump shaft 11 to pass through. A pump shaft connection that connects the pump shaft 11 to the output shaft of the motor assembly and supports the pump shaft 11 is disposed within a space 33 formed by an inner surface 37 of the cone housing 34 that faces the motor assembly. An opposite outer surface 39 of the cone housing 34 defines with the pump sleeve 22 a water space 35 in fluid communication with the inlet opening 32 for receiving water entering via the inlet opening 32 from outside the centrifugal pump. According to the present application, the water inlet 32 includes a plurality of water inlet groups spaced apart in the circumferential direction of the pump sleeve 22, each water inlet group including a plurality of water inlets densely distributed.
The plurality of impeller stage sets 200 included in the impeller section 50 and mounted within the pump sleeve 22 are described below. The illustrated impeller section 50 of the centrifugal pump comprises 4 impeller stage groups 200, of course the number of impeller stage groups of the centrifugal pump is not limited to 4, but may be varied according to actual requirements.
The impeller stage group 200 in the impeller section 50 includes a stationary support housing 60 and a inducer housing 250. In the axial direction, the deflector housing 250 is closer to the motor assembly and the water intake section 30 than the support housing 60, i.e. the deflector housing 250 is located below the support housing 60 during use of the centrifugal pump in a vertical configuration. The support casing 60 and the guide casing 250 in the impeller stage group 200 are engaged with each other in the axial direction, attached together, define together an impeller cavity penetrating in the axial direction, and the guide casing 250 of the previous impeller stage group 200 is attached together with the support casing 60 of the next impeller stage group 200 in two impeller stage groups 200 arranged adjacently in the vertical direction. The impeller stage set 200 also includes an impeller 70 positioned within the impeller cavity, the impeller 70 being engaged with the pump shaft 11 and driven to rotate synchronously by the pump shaft 11. In the field of centrifugal pumps, the impeller 70 is typically splined to the pump shaft 11, and the pump shaft 11 includes six splines 111 evenly distributed in the circumferential direction.
Fig. 2 shows a longitudinal section through the impeller stage group of the centrifugal pump of fig. 1. The impeller 70 includes a cylindrical hub 72 and a tapered wall 74 (opposite to the direction of extension of the cone housing 34 and thus also referred to as a "forward tapered wall") extending radially outwardly and axially upwardly from the hub 72, for example, near an upper end thereof, and vanes 76 extending helically from a lower surface 79 of the tapered wall 74, an impeller seat 78 being fixedly attached to the outer periphery of the vanes 76. The hub 72, tapered wall 74, vanes 76 and impeller seat 78 of the impeller 70 collectively define a centrifugal passageway 75 that allows water to flow therethrough. In accordance with the principles of the present application, the impeller seat 78 and other portions of the impeller 70 may be integrally formed or may be separately formed and then attached together by any suitable method, such as ultrasonic welding. The impeller seat 78 of the impeller 70 includes a cylindrical base 782 and a forwardly tapered wall 784 extending radially outwardly and axially upwardly inclined from the upper end of the cylindrical base 782.
The hub 72 defines a central bore 71, the central bore 71 being adapted for splined engagement with the pump shaft 11 such that the pump shaft 11 drives the impeller 70 such that the impeller 70 rotates synchronously with the pump shaft 11. The lower end of the hub 72 defines an axially downward, i.e., toward the central support end surface 73, and the impeller seat 78, and in particular the cylindrical base 782 thereof, defines an outer support end 77. The outer support end 77 includes one radial end face parallel to the axial direction and two axial end faces perpendicular to the axial direction.
The inducer housing 250 of the impeller stage set 200 includes a central portion 252 having a central bore that allows the pump shaft 11 to extend therethrough, an outer peripheral portion 254, and vanes 256 extending radially between the central portion 252 and the outer peripheral portion 254. The deflector channel 55 is defined by the central and peripheral portions 252, 254 of the deflector housing 250 and the adjacent outer stationary seal ring 98. The outer stationary seal ring 98 includes a radial contact 263 parallel to the axial direction and an axial contact 264 perpendicular to the axial direction. The radial contact portion 263 and the cylindrical base portion 782 define a first space 265 therebetween. The axial contact portion 264 and the cylindrical base portion 782 define a second space 266 therebetween. The width of the first space 265 in the radial direction is smaller than the width of the second space 266 in the axial direction. The second space 266 may function as a pressure balance. Specifically, during operation of the centrifugal pump, water that attempts to invade the diversion channel 55 from outside the impeller 70 via the second space 266 and the first space 265 is reduced in velocity after entering the second space 266 so as not to continue to enter the first space 265, i.e., the water is blocked in the second space 266. At the same time, the water in the second space 266 is thrown out by the centrifugal force, thereby forming an internal water pressure against the external water pressure, so that the impeller 70 can reduce the radial force generated by the water. In addition, the water pressure balance also enables a seal to be always present between the impeller 70 and the guide casing 250, and the seal is not disabled due to the high-speed rotation of the impeller.
In an upward direction toward the impeller 70, the central portion 252 of the inducer housing 250 defines a central abutment end face 262, the central abutment end face 262 being configured to always be in abutting contact with the central support end face 73.
In the non-operational state of the centrifugal pump, the impeller 70 is fitted in an axial impeller cavity defined by the support housing 60 and the inducer housing 250. The center support end surface 73 is in abutting contact with the center abutment end surface 262 such that the inducer 250 provides support to the impeller 70.
In the operating state of the centrifugal pump, the impeller 70 rotates at a high speed along with the pump shaft 11 (not shown in fig. 2), and the centrifugal force generated by the rotation of the impeller 70 is sucked from the guide passage defined by the guide housing 250 by the centrifugal force, enters the centrifugal passage 75 of the impeller 70, and is thrown into the guide passage 55 of the next impeller stage group 200.
An annular gap is defined between the periphery of the impeller seat 78 of the impeller 70, and in particular the upper end periphery of the positively tapered wall 784 thereof, and the support housing 60, which allows impurities, such as silt, in the water to settle downwardly. The sediment in the water flow flowing in the centrifugal channel 75 passes through the annular gap and then enters the impurity collection space defined jointly by the support housing 60, the guide housing 250 and the impeller seat 78 of the impeller stage group 200.
In the high-speed operation state of the centrifugal pump, the center support end surface 73 and the center contact end surface 262 are always kept in contact. In addition to providing support to the impeller 70, this abutment also receives axial forces from the impeller 70, and the transmission of the axial forces causes friction between the two end surfaces 73 and 262 that are in contact with each other. Any surface treatment of the end faces 73 and 262 may be used in order to reduce the effect of the friction thereby on the power and efficiency of the centrifugal pump. In one embodiment, an anti-friction coating may be applied to the end faces 73 and 262. In the illustrated embodiment, rather than simply applying an anti-friction coating to the surface, additional components made of an anti-friction material are provided to the impeller 70 and the inducer housing 250, respectively, to provide the end surfaces 73 and 262. For example, in FIG. 2, a ceramic center dynamic seal ring 92 is embedded within the hub 72 to provide the friction end face 73 and a tungsten steel center static seal ring 94 is embedded within the deflector housing 250 to provide the friction surface 262.
Fig. 3 shows a perspective view of the impellers of the impeller stage group of fig. 2. Fig. 4 shows an enlarged perspective view of section a of the impeller of fig. 3. As shown, the impeller seat 78 includes a plurality of water slingers 785 disposed radially outwardly of the outer support end 77 at a lower end thereof. A plurality of water slingers 785 are arranged circumferentially of the deflector housing 250. Each of the plurality of water slingers 785 includes two sides that are arranged at an angle. The angle between the two sides is between 50 DEG and 70 deg. In the high-speed operation state of the centrifugal pump, the plurality of water slingers 785 slings water out to form kinetic energy against external water pressure to reduce water leakage, and simultaneously, the impeller is brought into a dynamic floating state in the high-speed operation state of the centrifugal pump to reduce frictional resistance and vibration of the impeller stage group 200.
It will be appreciated by those skilled in the art that in order to increase pump efficiency, reduce friction losses, the abutting end surfaces 73 and 262 may be provided in any suitable manner, not limited to the forms described above by the impeller and the water intake seat themselves, or by the application of an anti-friction coating to the impeller and the water intake seat, or by additional parts made of embedded special materials, etc., but that the material of the applied anti-friction coating or embedded additional parts is not limited to those mentioned above.
The length of the hub 72 of the impeller 70 of each impeller stage group 200 in the axial direction is designed to extend beyond the support housing 60 of that impeller stage group 200 at a first axial end in an axial direction away from the motor assembly, extend into the inducer housing 250 at a second axial end opposite the first axial end and terminate in a central abutment end face 262.
The center support end surface 73 is always in abutting contact with the center abutment end surface 262. In the operating state of the centrifugal pump, the axial forces to which the impeller 70 is subjected are transmitted to the deflector housing 250 via abutment of the end surfaces 73 and 262, and thereafter to the pump sleeve 22. In this way, the axial forces experienced by the impellers 70 in all impeller stage groups are each transferred to the pump sleeve 22 so that no superposition of axial forces occurs between the vertically arranged impeller assemblies.
During operation of the centrifugal pump, water enters the water outlet section 40 after passing through the water inlet section 30 and the plurality of impeller stage groups 200. The water discharge section 40 includes an uppermost inducer housing 250 coupled to the support housing 60 of the last impeller stage group 200, a one-way valve 300 mounted to the uppermost inducer housing 250, and an outlet seat 310 (shown in FIG. 1) coupled to the pump sleeve 22 and defining a water discharge orifice 312.
During operation of the centrifugal pump, the output shaft of the motor assembly drives the pump shaft 11 to rotate, and the pump shaft 11 drives the impellers 70 of all the impeller stage groups to rotate synchronously. Under the suction created by the rotation of the impeller 70, water enters the water space 35 of the water intake section 30 from outside the centrifugal pump via the water intake holes 32 in the pump sleeve 22 and then into the impeller stage set 200. In the impeller stage set 200, water flows sequentially through the inducer passage defined by the inducer housing 250 and the centrifugal passage 75 defined by the impeller 70, into the next impeller stage set 200, and so on. After the water is "thrown" out of the centrifugal channel 75 of the last impeller stage group 200, it leaves the centrifugal pump via the flow guide channel of the uppermost flow guide housing 250, opening the one-way valve 300, via the water outlet 310 defined by the outlet seat 310.
As described above, the axial forces experienced by the impellers 70 in each impeller stage group 200 are transferred to the pump sleeve 22 via contact of the central support end face with the corresponding central abutment end face without being superimposed on the underlying adjacent impeller stage group 200, which would otherwise increase the axial forces experienced by the underlying impeller stage group 200. Such an arrangement reduces pump power losses as the impeller 70 rotates. On the other hand, by performing the surface treatment on the abutting end face in accordance with the above, the lost pump power can be further reduced, and the pump work efficiency can be improved.
The centrifugal pump adopts a motor structure component with the output rotation speed of 12000 or higher, adopts a pump body component structure schematically shown in the diagram, and can obtain the water output lift of about 300m by only configuring 5 impeller stage groups. At this time, the total height of the centrifugal pump is only about 1 m. Even if the controller of the centrifugal pump is accommodated inside the centrifugal pump, the total height of the centrifugal pump is only about 1.5m. Compared with the traditional centrifugal pump for deep wells, the height of the pump is shortened by one half to two thirds, and the height shortening means that the weight of the centrifugal pump is greatly reduced. The structure makes the deep well centrifugal pump widely applied, simpler and easier.
Although the application has been described above with reference to the embodiments shown in the drawings, it will be apparent to one of ordinary skill in the art that other embodiments and examples may perform similar functions and/or achieve similar results. It is therefore intended that all such equivalent embodiments and examples be within the spirit and scope of the present application, and that all such equivalent embodiments be covered by the following non-limiting claims for all purposes.
Claims (10)
1. A sealing structure for a centrifugal pump, the centrifugal pump comprising:
a motor assembly providing a rotational movement,
A pump shaft (11) driven by the output shaft of the motor assembly, and
A pump body assembly (20),
Wherein the pump body assembly comprises a pump sleeve (22) and a plurality of impeller stage groups (200) housed within the pump sleeve, the impeller stage groups (200) comprising: a support housing (60) and a guide housing (250) attached together in an axial direction to define an impeller cavity, and an impeller (70) housed within the impeller cavity to be driven by a pump shaft to rotate in synchronism therewith,
Wherein the impeller (70) comprises: a hub (72) defining a central bore for engagement with the pump shaft, and a tapered wall (74) extending radially outwardly and axially upwardly from the hub, a vane (76) extending helically from a lower surface of the tapered wall, and an impeller seat (78) attached to an outer periphery of the vane (76), the impeller seat (78) defining an outer support end (77) at a lower end thereof, the outer support end (77) comprising one radial end face and two axial end faces,
It is characterized in that the method comprises the steps of,
The sealing structure comprises a dynamic sealing structure and a water throwing groove sealing structure,
The dynamic sealing structure comprises an outer static sealing ring (98), the outer static sealing ring (98) comprises a radial contact part (263) parallel to the axial direction and an axial contact part (264) perpendicular to the axial direction, wherein a first space (265) is defined between the radial contact part (263) and a cylindrical base part (782) of an impeller seat (78) of an impeller (70) of a centrifugal pump, a second space (266) is defined between the axial contact part (264) and the cylindrical base part (782), wherein the width of the first space (265) in the radial direction is smaller than the width of the second space (266) in the axial direction,
The water slinger sealing structure comprises a plurality of water slingers (785) arranged at the lower end of an impeller seat (78) and radially outside the outer support end (77), wherein the water slingers (785) are arranged along the circumference of the diversion shell (250).
2. The seal structure of claim 1, wherein,
Each of the plurality of water slingers (785) includes two sides arranged at an angle,
The angle between the two side edges is between 50 DEG and 70 deg.
3. A sealing structure according to claim 1 or 2, wherein,
The flow guiding housing (250) of the impeller stage set (200) comprises a central portion (252) having a central bore allowing a pump shaft to extend therethrough, a peripheral portion (254) axially engaged with the support housing (60), and a vane (256) extending helically between the central portion (252) and the peripheral portion (254), the central portion (252), the peripheral portion (254) and the vane (256) defining a flow guiding channel (55) of the impeller stage set (200).
4. A sealing structure according to claim 3, wherein,
The impeller seat (78), the conical wall (74) and the blades (76) define a centrifugal channel (75), the hub (72) defines a central support end surface (73) perpendicular to the axial direction, the central support end surface (73) is defined by the hub (72) of the impeller (70) or a central dynamic seal ring (92) embedded at the lower end of the hub (72),
The deflector housing (250) includes a central abutment end surface (262) in constant abutting contact with the central support end surface (73), and
The diversion channel (55) is in fluid communication with the centrifugal channel (75).
5. The seal arrangement of claim 4, wherein the center movable seal ring (92) is constructed of tungsten steel.
6. The sealing structure of claim 4, wherein the central portion (252) is a deflector seat formed separately and attached to the peripheral portion.
7. The sealing structure according to claim 6, characterized in that the central abutment end surface (262) is provided by the flow guide seat or a central static sealing ring (94) embedded in the flow guide seat.
8. The seal arrangement of claim 4, wherein a first axial end of the hub portion (72) in an axial direction away from the motor assembly extends beyond the support housing (60) and terminates within the support housing (60) at a second axial end opposite the first axial end in the central abutment end face (262).
9. The seal arrangement of claim 8, wherein the impeller seat (78) and the support housing (60) define an annular gap.
10. The seal arrangement of claim 9, wherein the support housing (60), the deflector housing (250) and the impeller seat (78) together define an impurity collection space for receiving impurities from the annular gap.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110171359.5A CN114857035B (en) | 2021-02-04 | 2021-02-04 | Sealing structure for centrifugal pump |
| PCT/CN2021/117959 WO2022166205A1 (en) | 2021-02-04 | 2021-09-13 | Sealing structure for centrifugal pump |
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| CN214533584U (en) * | 2021-02-04 | 2021-10-29 | 浙江凯博瑞汽车零部件有限公司 | Sealing structure for centrifugal pump |
| CN214577901U (en) * | 2021-02-04 | 2021-11-02 | 温岭正峰数字机电科技有限公司 | Water throwing groove sealing structure for centrifugal pump |
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| JPH0326898A (en) * | 1989-06-21 | 1991-02-05 | Hitachi Ltd | centrifugal pump |
| CN2725588Y (en) * | 2004-05-13 | 2005-09-14 | 北京中水科工程总公司科禹泵制造厂 | High temperature resistant hot water circulation pump |
| DE602006015076D1 (en) * | 2005-09-19 | 2010-08-05 | Ingersoll Rand Co | |
| WO2012003386A2 (en) * | 2010-06-30 | 2012-01-05 | Schlumberger Canada Limited | Durable pumps for abrasives |
| EP2472055B1 (en) * | 2010-12-30 | 2013-08-07 | Welltec A/S | Artificial lift tool |
| CN202789583U (en) * | 2012-07-04 | 2013-03-13 | 陕西扶龙机电制造有限公司 | High-lift floating type impeller submersible pump for well |
| WO2015023636A1 (en) * | 2013-08-13 | 2015-02-19 | Schlumberger Canada Limited | Electric submersible pump with fluid coupling |
| CN103775386B (en) * | 2014-01-26 | 2017-12-05 | 潍柴动力股份有限公司 | A kind of engine water pump |
| CN203939721U (en) * | 2014-06-23 | 2014-11-12 | 温岭市天赐机电有限公司 | Deep-well pump |
| US10533578B2 (en) * | 2015-10-12 | 2020-01-14 | Baker Hughes, A Ge Company, Llc | Metal-to-metal sealing for diffusers of an electrical submersible well pump |
| CN110454410B (en) * | 2019-08-19 | 2024-04-26 | 浙江雅弗泵业股份有限公司 | Bending-proof pressure-loss-proof deep well pump |
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| CN214533584U (en) * | 2021-02-04 | 2021-10-29 | 浙江凯博瑞汽车零部件有限公司 | Sealing structure for centrifugal pump |
| CN214577901U (en) * | 2021-02-04 | 2021-11-02 | 温岭正峰数字机电科技有限公司 | Water throwing groove sealing structure for centrifugal pump |
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