WO2022166203A1

WO2022166203A1 - Centrifugal pump

Info

Publication number: WO2022166203A1
Application number: PCT/CN2021/117957
Authority: WO
Inventors: 朱世军; 连勇斌; 蒋焱
Original assignee: 钱江集团温岭正峰动力有限公司
Priority date: 2021-02-04
Filing date: 2021-09-13
Publication date: 2022-08-11

Abstract

A centrifugal pump, comprising a pump body assembly (20), wherein the pump body assembly (20) comprises a pump sleeve (22) and a plurality of impeller stage sets (B1-B5); each impeller stage set comprises a support body assembly (300), a guide vane cavity assembly (200), and an impeller assembly (100); the impeller assembly (100) comprises an impeller hub (110), an impeller (120) and an impeller seat (130); a lower end face of the impeller hub (110) is attached to an anti-wear accessory (150) defining a rotary joint face (152); an impeller axial support assembly (200 or 200') comprises an outer shell (210), an inner shell (220), a guide vane (230) connected between the outer shell (210) and the inner shell (220), and a stationary support member (250) attached to the inner shell (220); and the stationary support member (250) comprises a stationary joint face (254) joined with the rotary joint face (152) such that an axial force of the impeller assembly (100) is transferred to the inner shell (220) and then to the pump sleeve (22).

Description

centrifugal pump

This application claims priority to the following Chinese patent applications, the entire contents of which are incorporated herein by reference.

序号serial number	申请日application date	申请号Application Number	名称name
11	2021-02-042021-02-04	202110157911.5202110157911.5	离心泵 centrifugal pump
22	2021-02-042021-02-04	202120325563.3202120325563.3	离心泵centrifugal pump

technical field

The present application relates to the technical field of centrifugal pumps, in particular to a multi-stage centrifugal pump for deep wells with high rotational speed and high lift.

Background technique

The centrifugal pump for deep well generally includes a motor assembly and a pump body assembly including an impeller driven to rotate by a pump shaft. The pump shaft speed of the traditional centrifugal pump is generally around 3000rpm. If the head of the water output by the centrifugal pump reaches 300m, the height of the centrifugal pump may reach 3m. Therefore, this kind of deep well pump is large and heavy.

Centrifugal pumps for deep wells are mostly used for agricultural irrigation, and the operating environment is usually at a depth ranging from 100m to 500m underground. In applications with harsh natural environments such as mountains, it is very inconvenient to operate. In particular, for the handling of centrifugal pumps alone, workers need to manually lift to the top of the mountain, which may take several hours, or even a day, to install the huge and cumbersome centrifugal pump to the bottom of the well hundreds of meters deep and the subsequent Possible repairs are very difficult. This largely limits the application of centrifugal pumps.

In the improvement process of the pump, in order to increase the lift of the centrifugal pump, the method of increasing the diameter of the impeller is usually adopted, which further increases the volume and weight of the pump, and aggravates the above-mentioned inconvenience of the pump.

It is desirable to simplify the structure of the pump.

SUMMARY OF THE INVENTION

The purpose of the present application is to provide a centrifugal pump for deep wells with high power and high head, but with reduced volume and weight.

To this end, the present application provides a centrifugal pump, comprising a pump sleeve and a plurality of impeller stages housed in the pump sleeve, each impeller stage group comprising: a pump shaft driven by a pump shaft of the centrifugal pump to rotate therewith An impeller assembly, an impeller axial support assembly that surrounds the lower half of the impeller assembly and provides axial support, and a support body assembly that surrounds and provides support to the upper half of the impeller assembly, the impeller axial support assembly Mechanically connected with the support body assembly to form an impeller cavity for accommodating the impeller assembly, wherein:

The impeller assembly includes an impeller hub defining an impeller hub for engagement with the pump shaft, an impeller extending radially outwardly from the impeller hub, and an impeller seat attached to a radially outer periphery of the impeller, the lower end face of the impeller hub having a lower end surface attached to define the impeller hub. anti-wear attachments out of the rotating joint surface,

The impeller axial support assembly includes an outer casing mechanically connected to the support assembly and attached to the pump sleeve, an inner casing surrounding a portion of the outer peripheral surface of the impeller hub, and an outer casing connected to the inner casing guide vanes between, and a stationary support attached to the inner housing, the stationary support including a stationary engagement surface that engages the rotating engagement surface so that axial forces of the impeller assembly are transmitted to the inner housing and then to the pump sleeve.

In one embodiment, the anti-wear attachment is embedded in a groove formed on the lower end face of the impeller hub, or attached to at least a portion of the lower end face of the impeller hub.

In one embodiment, the anti-wear attachment is a tungsten steel ring.

In one embodiment, the stationary support is attached to the inner housing directly or via an intermediate piece.

In one embodiment, the stationary support is a ceramic ring.

In one embodiment, the impeller and impeller seat define an impeller passage, and the outer casing, inner casing and guide vanes define a flow guide passage in fluid communication with the impeller passage.

In one embodiment, the impeller includes a tapered portion extending radially outward from an axial position of the outer peripheral surface of the impeller hub and expanding upward in the axial direction, and a tapered portion extending from the tapered portion. The lower surface is a helically extending blade, and the impeller seat is attached to the radially outer periphery of the blade.

In one embodiment, the angle between the lower surface and the axial direction is between 40° and 70°.

In one embodiment, the outer casing of the impeller axial support assembly is joined to the impeller seat by an intermediate ring, the intermediate ring including an axial extension extending generally in the axial direction and transverse to the axial extension from Its radially outwardly extending radially extending portion is located radially inside the impeller seat and defines a first space therebetween, and the radially extending portion is located at the radially inner portion of the impeller seat. A second space is defined below and between the two.

In one embodiment, the radially outermost end of the vane seat of the impeller of each impeller stage and the corresponding support member assembly define an annular gap through which impurities in the water can pass.

In one embodiment, the plurality of impeller stages includes a first impeller stage closest to the motor assembly of the centrifugal pump, the impeller axial support assembly corresponding to the first impeller stage is an inlet seat assembly, The support body assembly of the first impeller stage is radially connected to the vane cavity assembly of the adjacent impeller stage above it.

In one embodiment, the plurality of impeller stages includes other impeller stages located above the first impeller stage, and the impeller axial support assemblies corresponding to the other impeller stages are guide vane cavity assemblies.

In one embodiment, the pump shaft is a six-toothed pump shaft comprising six key teeth distributed in the circumferential direction.

In the centrifugal pump of the present application, the axial force borne by the impeller assembly in each impeller stage group is transmitted to the guide vane cavity assembly through the impeller, and then to the pump sleeve, and will not be superimposed on the adjacent impeller stage group below. , there will be no superposition of axial force, which reduces the loss of pump efficiency and pump power. Under the condition of achieving the same head, the height and weight of the pump are reduced by about two-thirds, which greatly improves the application breadth and ease of the centrifugal pump.

Description of drawings

The foregoing and other features, advantages and benefits of the present application will be described in detail below in conjunction with exemplary embodiments of the present application with reference to the accompanying drawings. It should be understood that the drawings are not to scale, and are merely used to illustrate the principles of the application and are not intended to limit the application to the embodiments illustrated. The components shown in the drawings do not necessarily exist in all embodiments of the present application, and components not shown in the drawings may exist in some embodiments of the present application.

1 is a longitudinal cross-sectional view of an exemplary centrifugal pump of the present application;

Fig. 2 is a partial exploded view of the centrifugal pump of Fig. 1;

3 is an enlarged view of an impeller assembly and a guide vane cavity assembly of a second impeller stage of the centrifugal pump of FIG. 1;

4 is a cross-sectional view of a pump shaft of an exemplary centrifugal pump of the present application.

Detailed ways

The centrifugal pump of the present application will be described in detail below with reference to the accompanying drawings. Parts that are structurally or functionally identical or similar have the same reference numerals throughout the drawings.

1 and 2 show an axial cross-sectional view and a partial exploded view, respectively, of the centrifugal pump of the present application. Generally, a centrifugal pump includes a motor assembly 10 and a pump body assembly 20 . The motor assembly 10 includes a motor housing and a motor, such as an electric motor, accommodated in the motor housing and capable of outputting a high rotational speed. Auxiliary systems that provide auxiliary functions for the operation of the motor, such as cooling systems, are also located within the motor housing. The pump body assembly 20 includes a pump sleeve 22 and a plurality of impeller stages housed within the pump sleeve 22 . The output shaft of the motor drives the impellers of each impeller stage group in the centrifugal pump to rotate through the pump shaft 11 of the centrifugal pump. In the illustrated embodiment, the pump shaft 11 adopts a six-tooth pump shaft, and FIG. 4 shows an enlarged cross-sectional view of the pump shaft 11 , wherein the pump shaft 11 includes a body 111 and uniformly arranged from the outer peripheral surface of the body 111 Six protrusions 113 .

In the present application, for the convenience of description, the direction in which the pump shaft 11 extends is defined as an axial direction, and the circumferential direction extends around the axial direction. The centrifugal pump of the present application is usually placed vertically during use, so the axial direction is also referred to as the vertical direction, the direction/end toward the motor assembly 10 in the axial direction is referred to as the lower/lower end, and the opposite direction/end The part is called the upper/upper end. In a plane perpendicular to the axial direction, with reference to the central axis of the pump shaft 11 defining the axial direction, the direction from the pump sleeve 22 toward the central axis of the pump shaft 11 is referred to as radially inward, and on the contrary, from The direction of the central axis of the pump shaft 11 toward the pump sleeve 22 is referred to as radially outward.

Referring again to FIGS. 1 and 2 , in the axial direction, from bottom to top, the pump body assembly 20 sequentially includes a water inlet section 30 , an impeller section 50 composed of a plurality of impeller stages, and a water outlet section 40 .

In the water inlet section 30 , the pump sleeve 22 is provided with water inlet holes 32 distributed in the circumferential direction, and, in the water inlet section 30 , a conical housing 34 is provided in the pump sleeve 22 . The cone housing 34 is configured as an inverted cone open towards the motor assembly 10 and includes a central hole allowing the pump shaft 11 to pass through. The pump shaft connection that connects the pump shaft 11 to the output shaft of the motor assembly 10 and supports the pump shaft 11 is provided in the space 33 formed by the inner surface 37 of the cone housing 34 facing the motor assembly 10 . The opposite outer surface 39 of the cone housing 34 and the pump sleeve 22 define a water inlet space 35 in fluid communication with the water inlet hole 32 for receiving water entering via the water inlet hole 32 from outside the centrifugal pump. According to the present application, the water inlet holes 32 include a plurality of water inlet hole groups that are spaced apart along the circumferential direction of the pump sleeve 22, and each water inlet hole group includes a plurality of water inlet holes that are densely distributed.

In the impeller section 50 , five impeller stages B1 - B5 arranged in series in the axial direction are successively mounted in the pump sleeve 22 . Of course, the number of impeller stages of the centrifugal pump is not limited to 5, but can be changed according to actual needs. Herein, the impeller stage group located at the lowermost position of the centrifugal pump adjacent to the water inlet section 30 is referred to as the first impeller stage group, denoted by reference numeral B1; other impeller stage groups except the first impeller stage group Known as other impeller stage groups, designated by reference numerals B2-B5.

Typically, in a centrifugal pump including a plurality of impeller stage sets B1-B5 as illustrated, for other impeller stage sets B2-B5 other than the first impeller stage set B1 adjacent to the water inlet section 30 Said, each impeller stage group includes an impeller assembly 100 driven by the pump shaft 11 to rotate together, a guide vane cavity assembly 200 surrounding the lower half of the impeller assembly 100 and providing axial support, and surrounding the impeller assembly 100 The upper part of the support body assembly 300 that provides support for it. The first impeller stage group B1, that is, the lowermost impeller stage group has a slightly different structure because it is adjacent to and connected to the water inlet section 30 of the pump body assembly 20. The impeller assembly 100 of the first impeller stage group B1 also includes a surrounding The difference of the upper half of the support body assembly 300 is that the lower half of the impeller assembly 100 is axially supported by the inlet seat assembly 200 ′ whose structure is slightly different from the above-mentioned guide vane cavity assembly 200 .

Although the inlet seat assembly 200' that provides axial support to the impeller assembly 100 of the first impeller stage group B1 is different from the guide vane cavity assembly 200 that provides axial support to the impeller assemblies 100 of the other impeller stage groups B2-B5, Interface structure between the inlet seat assembly 200' and the impeller assembly 100 for the first impeller stage group B1 and between the support member assembly 300 and the vane cavity assembly 200 and impellers for the other impeller stage groups B2-B5 Assembly 100 and the interface structure with support assembly 300 are the same. In view of this, in the description herein, the inlet seat assembly 200' for the first impeller stage group B1 and the vane cavity assembly 200 for the other impeller stage groups B2-B5 are collectively referred to as "impeller axial support assemblies" . That is, each impeller stage group B1-B5 of the centrifugal pump of the present application includes an impeller assembly 100, a support body assembly 300 and an impeller axial support assembly 200 or 200'.

For each impeller stage, its support body assembly 300 and impeller axial support assembly are mechanically connected together to form an impeller cavity that accommodates and supports the impeller stage 100 . The support body assembly 300 of each impeller stage is mechanically connected to the impeller axial support assembly 200 or 200' of the adjacent impeller stage above it, so that the impeller stages are mechanically connected together. Likewise, for each impeller stage set, the impeller assembly 100 defines an impeller passage 125 (see FIG. 3 ) that allows water to flow therethrough, and the impeller

axial support assembly

200 or 200 ′ defines a flow guide passage in fluid communication with the impeller passage 125 . 225 (Figure 3). The impeller passages 125 of each impeller stage are in fluid communication with the guide passages 225 of the adjacent impeller stage above it, thereby forming a continuous water flow passage throughout the impeller section 50 . In other words, the impeller assemblies 110 and the impeller axial support assemblies 200 or 200' of all impeller stage groups B1-B5 together define the water flow channel.

The water outlet section 40 located at the opposite end of the water inlet section 30 includes the uppermost guide vane cavity assembly 410 connected to the support body assembly 300 of the last impeller stage B5, and a single vane cavity assembly 410 mounted on the guide vane cavity assembly 410. Valve assembly 420, and outlet seat assembly 430 (shown in FIG. 1) attached to pump sleeve 22 and defining outlet 432

FIG. 3 is a cross-sectional view illustrating the joint structure of the impeller assembly 100 and the impeller axial support assembly 200 in an enlarged form by taking the second impeller stage group B2 as an example. Those skilled in the art will understand that the joint structure of the impeller assembly 100 and the impeller axial support assembly 200 described below with respect to the second impeller stage set B2 is applicable to all other impeller stages of the centrifugal pump, including the first impeller stage set B1 .

The structure of the impeller assembly 100 and the support assembly 300 is the same for all impeller stages of the centrifugal pump. The impeller assembly 100 mainly includes an impeller hub 110 , an impeller 120 and an impeller seat 130 . The impeller hub 110 is generally cylindrical and defines a shaft hole 112 that allows the pump shaft 11 of the centrifugal pump to pass through and engage therewith. Generally, the impeller hub 110 and the pump shaft 11 can be engaged by a keying manner, and the keyway in the shaft hole 112 is schematically shown in FIG. 3 .

The impeller 120 includes a tapered portion 124 extending from an upper portion of the outer peripheral surface 114 of the impeller hub 110 , eg, from an axial position P in a radial direction outward, expanding upward in the axial direction, and a lower portion from the tapered portion 124 . Surface 123 has helically extending vanes 126 . The impeller seat 130 is located radially outside the impeller 120 and is circumferentially attached to the radially outer circumference or free end of the impeller 120 , in particular the blades 126 . The impeller seat 130 includes an axial base 132 and a flared portion 134 extending radially outward from the axial base 132 and axially upward. An impeller channel 125 allowing water to flow therethrough is formed between the impeller 120 and the impeller seat 130 . In one embodiment of the present application, the impeller 120 and the impeller hub 110 are integrally formed, and the impeller seat 130 is attached to the outer periphery of the impeller 120 for rotation with the impeller 120 in any manner known in the art. Those skilled in the art will appreciate that the impeller hub 110, the impeller 120, and the impeller seat 130 may be separately formed and then attached together, or any two or three of them may be integrally formed.

As described above, the vanes 126 of the impeller 120 protrude from the lower surface 123 of the tapered portion 124 . In one embodiment, the angle between the lower surface 123 and the horizontal plane is between 20° and 50°, in other words, the angle between the lower surface 123 and the central axis Z is between 40° and 70°.

An anti-wear attachment 150 is attached to the lower end face of the impeller hub 110 . The anti-wear attachment 150 may be attached and fixed to the lower end face of the impeller hub 110 in any suitable manner, including, but not limited to, interference fit, connection with fasteners, and any other connection manner known in the art. In the illustrated embodiment, the anti-wear attachment 150 is embedded in a groove formed on the lower end face of the impeller hub 110 . The lower end face 152 of the anti-wear attachment 150 provides a rotational interface with which the impeller axial support assembly 200 is engaged. In an embodiment not shown, it is contemplated that the anti-wear attachment 150 may be attached to a portion of the lower end face of the impeller hub 110 or cover the entire lower end face of the impeller hub 110 .

The impeller axial support assembly 200 includes an outer housing 210 adapted to mechanically engage and attach to the pump sleeve 22 of a support assembly 300 (not shown in FIG. 3 ) of the impeller stage, and a lower casing surrounding the impeller stage 100 . Half, in particular, the inner casing 220 of the lower part of the outer peripheral surface 114 of the impeller hub 110 , the guide vanes 230 extending between the inner casing 220 and the outer casing 230 , together with the inner casing 220 and the outer casing 210 to allow water flow through the guide vane channel 225.

In the illustrated embodiment, the middle piece 240 is fixedly attached to the inner housing 220, the stationary support base 250 that directly contacts and supports the impeller assembly 100 is attached to the middle piece 240 and remains stationary during operation of the centrifugal pump verb: move. The intermediate piece 240 and the stationary support 250 define shaft holes 242 and 252, respectively, that allow the pump shaft to pass through. The stationary support 250 includes an upper surface 254 to serve as a stationary engagement surface for contact with the rotational engagement surface provided by the lower end surface 152 of the anti-wear attachment 150 described above.

As shown in FIG. 3 , in the assembled state of the impeller assembly 100 and the impeller axial support assembly 200 , the lower end surface 152 of the anti-wear attachment 150 rotating with the impeller assembly 100 at high speed engages the upper surface 254 of the stationary ceramic support seat 250 . The anti-wear attachment 150 and the stationary support 250 form a dynamic sealing engagement between the contacting surfaces, preventing water in the water flow channel from entering the pump through the axial gap 270 between the inner housing 220 and the impeller hub 110 of the impeller assembly 110 shaft hole. In one embodiment, the anti-wear attachment 150 may be formed of a tungsten steel material, and the stationary support seat 250 may be formed of a ceramic material. The selection of these two materials enables friction between the relatively moving anti-wear attachment 150 and the stationary support seat 250 least resistance. Preferably, as shown in FIG. 3 , on the upper end surface 254 of the stationary support base 250 all the notches 262 are evenly distributed along the circumferential direction. The arrangement of the notches 262 avoids or greatly reduces the wear resistance of the anti-wear accessories 150 and the wear resistance caused by the high-speed rotation. The molecular binding force generated by the vacuum formed between the stationary stationary supports 250 greatly reduces the power loss of the centrifugal pump and improves the efficiency of the pump.

As shown, the outer housing 210 of the impeller axial support assembly 200 is joined to the axial base 132 of the impeller seat 130 of the impeller assembly 100 through an intermediate ring 280 . The intermediate ring 280 includes an axial extension 282 extending generally in the axial direction and a radial extension 284 extending radially outward therefrom transverse to the axial extension 282 . A first space 292 is defined between the axially extending portion 282 and the axial base portion 132 of the impeller seat 130 . A second space 294 is defined between the radial extension 284 and the axial base 132 . The width of the first space 292 in the radial direction is smaller than the width of the second space 294 in the axial direction. The second space 294 may play a role of pressure equalization. Specifically, during the operation of the centrifugal pump, the water from the space radially outside the impeller seat 130 trying to intrude into the water flow channel via the second space 294 and the first space 292 is greatly reduced in speed after entering the second space 294, so that it will not continue Entering the first space 292 , ie, most, if not all, water is blocked in the second space 294 . At the same time, under the action of centrifugal force, the water in the second space 294 is thrown out, thereby forming an internal water pressure that opposes the external water pressure, so that the impeller 120 may not bear the radial force generated by the water. In addition, the above-mentioned water pressure balance also keeps the impeller assembly 100, specifically, the impeller seat 130 and the outer casing 210 in a "sealed" state all the time, and the seal will not fail due to the high-speed rotation of the impeller.

In the non-operating state of the centrifugal pump, the impeller assembly 100 is assembled in the axial impeller cavity formed by the support member assembly 300 and the impeller axial support assembly 200 . The lower end face 152 of the anti-wear attachment 150 is in axial contact with the upper end face 254 of the stationary support 250 , and the impeller axial support assembly 200 axially supports the impeller assembly 110 and the support assembly 300 .

In the operating state of the centrifugal pump, the impeller assembly 100 is driven by the pump shaft 11 to rotate at a high speed in the axial impeller cavity, and the water is confined from the impeller axial support assembly 200 under the action of the suction force generated by the rotation of the impeller 120 . The guide channel 225 is sucked into the impeller channel 125 of the impeller 120 and then thrown into the guide channel 225 of the next impeller stage. At this time, the lower end surface 152 of the anti-wear attachment 150 rotating with the impeller assembly 100 at a high speed is in axial contact with the upper end surface 254 of the stationary stationary support 250 and is in sealing combination, and any axial force on the impeller assembly 120 is transmitted. to the stationary support 250 of the impeller axial support assembly 200 and then to the inner casing 220 and the outer casing 210 . The transmission of this axial force causes friction between the two end faces 152 and 254 that are in contact with each other. In order to reduce the effect of this friction on the power and efficiency of the centrifugal pump, any surface treatment measures may be applied to the end faces 152 and 254 in contact with each other. In one embodiment, an anti-friction coating may be applied to the end faces 152 and 254 . In the illustrated embodiment, tungsten steel and ceramic materials are selected to form the anti-wear attachment 150 and stationary support 250, respectively, to minimize frictional resistance and molecular binding resistance developed on the two surfaces.

In addition, as shown, the end 134a of the flared portion 134 of the impeller seat 130 of the impeller assembly 100 and the support body assembly 300 define an annular gap 80 (see FIG. 1 ) that allows impurities in the water, such as sediment, to settle down. . The sediment in the water flow in the impeller channel 125 passes through the annular gap 80 and then enters the impurity collection space 90 defined by the support member 300 of the impeller stage 100 , the outer casing 220 of the impeller axial support assembly 200 and the impeller seat 130 .

As described above, the axial force experienced by the impeller assembly 100 in each impeller stage is caused by the axial engagement of the lower end face 152 of the anti-wear attachment 150 with the upper end face 254 of the stationary support seat 250 of the impeller axial support assembly 200 . pass to the impeller axial support assembly 200 (or the inlet seat assembly for the first impeller stage set B1), and then to the pump sleeve 22, without being superimposed on the adjacent impeller stage set below, which would not Increasing the axial force borne by the lower impeller stage group will not produce the superposition of axial force. Such an arrangement reduces pump power losses due to rotational friction created by the superposition of axial forces of the impeller assembly 100 . On the other hand, the corresponding surface treatment of the above-mentioned contact end face or the selection of specific materials can further reduce the lost pump power and improve the working efficiency of the pump.

The centrifugal pump of the present application adopts a motor structure assembly with an output speed of up to 12,000 or higher, and adopts the pump body assembly structure as schematically shown in the figure. It only needs to configure 5 impeller stages, and a water output of about 300m can be obtained. lift. At this time, the total height of the centrifugal pump is only about 1m. Even if the controller of the centrifugal pump is accommodated inside the centrifugal pump, the overall height of the centrifugal pump is only about 1.5 m. Compared with the traditional centrifugal pump for deep wells, the height of the pump is shortened by one-half to two-thirds, which means that the weight of the centrifugal pump is greatly reduced. Such a structure makes the application of the deep well centrifugal pump wider, simpler and easier.

Although the present invention has been described above with reference to the embodiments shown in the figures, it will be apparent to those of ordinary skill in the art that other embodiments and examples may perform similar functions and/or achieve similar results. It is hereby contemplated that all such equivalent embodiments and examples are within the spirit and scope of the present invention, and for all purposes are intended to be covered by the following non-limiting claims.

Claims

A centrifugal pump, characterized in that it comprises a pump sleeve (22) and a plurality of impeller stage groups (B1-B5) accommodated in the pump sleeve, and each impeller stage group comprises: a pump shaft (B1-B5) of the centrifugal pump. 11) The impeller assembly (100) driven to rotate therewith, the impeller axial support assembly (200 or 200') surrounding the lower half of the impeller assembly (100) and providing axial support, and surrounding the impeller assembly ( 100) the upper half of the support body assembly (300) and provide support for it, the impeller axial support assembly (200 or 200') and the support body assembly (300) are mechanically connected together to form a accommodating impeller assembly (100) ) of the impeller cavity, where:

The impeller assembly (100) includes an impeller hub (110) defining an engagement with the pump shaft (11), an impeller (120) extending radially outward from the impeller hub (110), and an impeller (120) attached to the impeller (120). a radially outer peripheral impeller seat (130) with an anti-wear attachment (150) attached to the lower end face of said impeller hub (110) defining a rotational joint surface (152),

The impeller axial support assembly (200 or 200') includes an outer housing (210) mechanically connected to the support assembly (300) and attached to the pump sleeve (22), surrounding the impeller hub (110) an inner casing (220) of a part of the outer peripheral surface, and a guide vane (230) connected between the outer casing (210) and the inner casing (220), and a guide vane (230) attached to the inner casing (220) A stationary support (250) comprising a stationary engagement surface (254) engaged with the rotating engagement surface (152) such that the axial force of the impeller assembly (110) is transmitted to all The inner casing (220) is then passed to the pump sleeve (22).
The centrifugal pump according to claim 1, wherein the anti-wear attachment (150) is embedded in a groove formed on the lower end surface of the impeller hub (110), or attached to the impeller hub (110). ) on at least a portion of the lower end surface.
The centrifugal pump according to claim 2, wherein the anti-wear accessory (150) is a tungsten steel ring.
The centrifugal pump of claim 1, wherein the stationary support (250) is attached to the inner housing (220) either directly or via an intermediate piece (240).
The centrifugal pump of claim 4, wherein the stationary support (250) is a ceramic ring.
The centrifugal pump of claim 1, wherein the impeller (120) and the impeller seat (130) define an impeller passage (125), the outer casing (210), the inner casing (220) and the guide Vanes (230) define flow guide passages (225) in fluid communication with impeller passages (125).
The centrifugal pump according to claim 1, characterized in that the impeller (120) comprises an axial position (P) of the outer peripheral surface (114) of the impeller hub (110) starting from an axial position (P) outward in the radial direction and A tapered portion (124) extending upwardly expanding in the axial direction and vanes (126) extending helically from a lower surface (123) of the tapered portion (124), the impeller seat (130) is attached to The radial outer circumference of the vanes (126).
The centrifugal pump according to claim 7, wherein the angle between the lower surface (123) and the axial direction is between 40° and 70°.
The centrifugal pump according to any one of claims 1-8, wherein the outer casing (210) of the impeller axial support assembly (200) is joined to the impeller seat (130) through an intermediate ring (280). ), said intermediate ring (280) comprising an axial extension (282) extending generally in the axial direction and a radial extension (284) extending radially outward therefrom transverse to the axial extension (282), The axially extending portion (282) is located radially inside the impeller seat (130) and a first space (292) is defined therebetween, and the radially extending portion (284) is located in the impeller seat (130). 130) and a second space (294) is defined therebetween.
The centrifugal pump according to claim 9, wherein the radially outermost end (134a) of the guide vane seat (130) of the impeller (120) of each impeller stage group and the corresponding support member assembly (300) The gap defines an annular gap (80) through which impurities in the water are allowed to pass.
The centrifugal pump according to any one of claims 1-8, characterized in that the plurality of impeller stage groups comprise the first impeller stage group (B1) closest to the motor assembly of the centrifugal pump, corresponding to the The impeller axial support assembly of the first impeller stage group (B1) is an inlet seat assembly (200'), and the support body assembly (300) of the first impeller stage group (B1) is radially connected to its upper adjacent The vane cavity assembly (200) of the impeller stage group.
The centrifugal pump according to claim 11, wherein the plurality of impeller stage groups include other impeller stage groups located above the first impeller stage group (B1), corresponding to the impeller axial direction of the other impeller stage groups The support assembly is a vane cavity assembly (200).
The centrifugal pump according to any one of claims 1-8, wherein the pump shaft (11) is a six-toothed pump shaft including six key teeth (111) distributed in the circumferential direction.