WO2022166204A1 - 离心泵 - Google Patents

离心泵 Download PDF

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Publication number
WO2022166204A1
WO2022166204A1 PCT/CN2021/117958 CN2021117958W WO2022166204A1 WO 2022166204 A1 WO2022166204 A1 WO 2022166204A1 CN 2021117958 W CN2021117958 W CN 2021117958W WO 2022166204 A1 WO2022166204 A1 WO 2022166204A1
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WO
WIPO (PCT)
Prior art keywords
impeller
assembly
centrifugal pump
stationary
ceramic support
Prior art date
Application number
PCT/CN2021/117958
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English (en)
French (fr)
Inventor
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 (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Priority claimed from CN202110156817.8A external-priority patent/CN114857031A/zh
Priority claimed from CN202120325349.8U external-priority patent/CN214660924U/zh
Application filed by 钱江集团温岭正峰动力有限公司 filed Critical 钱江集团温岭正峰动力有限公司
Publication of WO2022166204A1 publication Critical patent/WO2022166204A1/zh

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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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage pumps
    • F04D1/08—Multi-stage pumps the stages being situated concentrically
    • 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
    • F04D29/02—Selection of particular materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type

Definitions

  • 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.
  • a centrifugal pump for deep wells generally includes a motor assembly and a pump body assembly having one or more impeller assemblies driven to rotate by a pump shaft.
  • the pump shaft speed of the traditional centrifugal pump is generally around 1300rpm. If the lift of the water output by the centrifugal pump reaches 130m, the height of the centrifugal pump may reach 3m. Therefore, this kind of deep well pump is bulky and heavy.
  • Centrifugal pumps for deep wells are mostly used for agricultural irrigation, and the operating environment is usually at a depth ranging from 110m 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.
  • the purpose of this application is to provide a novel centrifugal pump structure, which improves the efficiency of the centrifugal pump by reducing the frictional energy consumption between the rotating parts and the stationary parts in the centrifugal pump, thereby greatly reducing the volume and weight of the pump.
  • a centrifugal pump comprising:
  • An impeller assembly driven for rotation in an axial direction by a pump shaft, the impeller assembly including an impeller hub defining a shaft bore that engages the pump shaft, and attached to the impeller hub and radially outward from an outer peripheral surface of the impeller hub
  • the impeller extending in a spiral shape, the lower end face of the impeller hub is attached with a tungsten steel accessory, and the tungsten steel accessory includes a shaft hole that allows the pump shaft to pass through and a lower end face as a rotating joint surface;
  • an impeller axial support assembly (200, 200') that axially supports the impeller assembly and remains stationary, the impeller axial support assembly including a ceramic support that defines a shaft hole allowing the pump shaft to pass through, and is configured to frictionally engage with the lower end face of the tungsten steel attachment during operation of the centrifugal pump so that the axial force experienced by the impeller assembly is transmitted to the stationary engagement surface of the impeller axial support assembly.
  • the tungsten steel attachment is embedded in a notch formed on the lower end face of the impeller hub, or is attached to the lower end face of the impeller hub.
  • the stationary engagement surface includes a plurality of notches recessed into the ceramic support, the notches projecting radially outwardly from an inner surface of the ceramic support defining a shaft bore.
  • the plurality of notches are arranged evenly spaced in a circumferential direction around the axial direction.
  • the plurality of notches are recessed from the stationary engagement surface into the ceramic support to a depth between one quarter and one half of the axial thickness of the ceramic support .
  • the centrifugal pump includes a plurality of the impeller assemblies.
  • the impeller axial support assembly is an inlet seat support assembly.
  • the impeller axial support assembly is a guide vane cavity assembly
  • the guide vane cavity assembly further A stationary support defining the stationary joint surface is attached to the inner housing including an outer housing and an inner housing defining a vane channel.
  • the ceramic support is attached directly to the inner housing, or via an intermediate piece.
  • one or both of the tungsten steel attachment and the ceramic support are planar annular components.
  • the impeller extends from an upper portion of the outer peripheral surface of the impeller hub, and the impeller assembly further includes a jacket attached around the lower portion of the outer peripheral surface of the impeller hub, the jacket Define a lower end surface that is flush with the lower end surface of the tungsten steel attachment in the axial direction or extends downward slightly beyond the latter.
  • the stationary engagement surface of the ceramic support includes an inner annular stationary engagement portion and an outer annular stationary engagement portion that engage with the lower end surface of the tungsten steel attachment and the lower end surface of the sheath, respectively.
  • a plurality of notches recessed into the ceramic support are provided in the inner annular stationary engagement portion of the stationary engagement surface.
  • the lower end face has a radial width of between 1-5 mm in cross section perpendicular to the axial direction.
  • the centrifugal pump of the present application includes a plurality of impeller stages, and each impeller stage includes an impeller assembly that performs high-speed rotational motion and a stationary impeller axial support assembly that axially supports the impeller assembly, wherein the impeller assembly includes tungsten Steel attachment, the impeller axial support assembly includes a ceramic support, during the operation of the centrifugal pump, the lower end face of the tungsten steel attachment of the high-speed rotating impeller assembly is frictionally engaged with the upper end face of the ceramic support of the stationary impeller axial support assembly , a plane seal is formed, and the axial force borne by the impeller assembly is transmitted to the stationary impeller axial support assembly through this plane joint.
  • planar sealing engagement of the tungsten steel attachment and the ceramic support minimizes the friction between the two in the case of transmitting axial forces, and creates a vacuum between the two planes that are joined to create a barrier between the two.
  • the intermolecular force of relative rotation is the smallest. This reduces the resulting energy loss and increases the efficiency of the centrifugal pump.
  • FIG. 1 is a partially exploded perspective view of an exemplary centrifugal pump of the present application, wherein the arrangement of the impeller stages of the pump body assembly of the centrifugal pump is highlighted;
  • Figure 2 shows a cross-sectional view of the structural details of the impeller assembly and the impeller axial support assembly of the impeller stage group B3 marked in the centrifugal pump of Figure 1, constructed according to a first embodiment of the present application;
  • Figures 3a-3c are different views of a stationary support in the impeller axial support assembly of Figures 1 and 2;
  • FIG. 4 is an alternative embodiment of FIG. 2, constructed in accordance with a second embodiment of the present application.
  • the centrifugal pump of the present application generally includes a motor assembly 10 and a pump body assembly 20 .
  • the motor assembly 10 mainly includes a motor housing and a motor accommodated in the motor housing and capable of outputting a high rotational speed.
  • the structure and structural details of the motor assembly 10 are not the focus of the present application. In order to highlight the key points, FIG. 1 only schematically shows the motor assembly 10 , and does not show its internal details.
  • the pump body assembly 20 includes a pump sleeve 22 and at least one, eg, a plurality of impeller stages housed within the pump sleeve 22 .
  • the pump shaft 11 protrudes from the motor assembly 10 to transmit the rotational motion output by the motor to the impeller assemblies of each impeller stage group in the pump body assembly 20 .
  • the pump shaft 11 defines an axial direction Z including an upward direction and a downward direction.
  • the centrifugal pump of the present application is generally placed upright when used. Therefore, the directional terms used in the description of this application all refer to the working state after being assembled in the centrifugal pump and placed vertically.
  • the "upper” part or the “upper” side, or the “lower” part or the “lower” side respectively refers to the upper part or the upper part of the part after assembly into the centrifugal pump and when the assembled centrifugal pump is in the vertical working state , or lower and lower.
  • the pump body assembly 20 includes in turn: the water inlet section closest to the motor assembly 10 , for example, in the exploded view of FIG. 1 , this section includes the portion of the pump sleeve 22
  • the water inlet section 32 including the water inlet hole 31, the components accommodated in the water inlet section 32 of the pump sleeve 22, including but not limited to the connection structure connecting the pump shaft 11 to the motor output shaft, etc.; an impeller section consisting of a plurality of impeller stage groups B1-B5 arranged one above the other in series, for example, in the exploded view of the 5-stage exemplary centrifugal pump of FIG.
  • the motor drives the pump shaft 11 to rotate, water enters the centrifugal pump through the water inlet hole 31 of the water inlet section, and the impeller assemblies in the impeller stages arranged in series rotate at high speed to transport the water to the water outlet section, Exit the centrifugal pump via the outlet mouth body assembly 42 .
  • each An 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 part of the impeller assembly 100 and providing axial support, and surrounding the upper half of the impeller assembly 100 and Support body assembly 300 to which support is provided.
  • 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 of the pump body assembly 20.
  • the impeller assembly 100 of the first impeller stage group B1 also includes a surrounding upper portion. The difference is that the lower part of the impeller assembly 100 is axially supported by the inlet seat assembly 200 ′ whose structure is slightly different from that of the guide vane cavity assembly 200 described above.
  • 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
  • Axial engagement and support structure between inlet seat assembly 200' for first impeller stage group B1 and impeller assembly 100 of first impeller stage group B1 and vane cavity assembly for other impeller stage groups B2-B5 The axial engagement and support structures between the 200 and their impeller assemblies 100 are the same.
  • 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" .
  • the focus of the present application is on the joint structure between the high-speed rotating impeller assembly 100 and the stationary impeller axial support assembly 200' or 200 in each impeller stage group B1-B5.
  • the impeller assembly 100 of the present application includes a tungsten steel attachment
  • the impeller axial support assembly includes a ceramic support that is in contact with the tungsten steel attachment.
  • the high-speed rotating impeller assembly and the stationary impeller axial support assembly minimize the friction between the joint surfaces through the joint or combination of the tungsten steel attachment and the ceramic support, and the joint surface is in the seal. , and thus the minimization of the molecular binding force between the two surfaces under the condition of forming a vacuum, thereby achieving the minimization of the above-mentioned unfavorable forces.
  • FIG. 2 shows the impeller assembly 100 included in the impeller stage group B3 marked in FIG. 1 and the impeller axial support assembly, that is, the guide vane cavity assembly 200 .
  • the support and engagement structures between the impeller assembly 100 and the impeller axial support assembly 200 described below are equally applicable to all other impeller stage groups B1, B2, B4 and B5.
  • 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.
  • the impeller hub 110 and the pump shaft 11 can be engaged by a keyed manner, and the keyway in the shaft hole 112 is schematically shown in FIG. 2 .
  • the impeller 120 extends helically from the upper portion of the outer peripheral surface 114 of the impeller hub 110 radially outward and toward the upper end.
  • the impeller seat 130 is located radially outward of the impeller 120 and surrounds the outer circumference of the impeller 120 .
  • An impeller channel 125 allowing water to flow therethrough is formed between the impeller 120 and the impeller seat 130 .
  • 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.
  • the impeller hub 110 , the impeller 120 and the impeller seat 130 may be formed separately and then attached together, or at least two or three of them may be integrally formed.
  • a sheath 140 is attached to the lower portion of the outer peripheral surface 114 of the impeller hub 110 , and a tungsten steel attachment 150 is attached to the lower end surface of the impeller hub 110 .
  • the manner in which the sheath 140 and the tungsten steel attachment 150 are attached to the outer peripheral surface 114 and the lower end surface of the impeller hub 110 may include, but are not limited to, interference fit, connection with fasteners, etc., any known connection in the art.
  • the sheath 140 may be formed from a stainless steel material.
  • the lower end face 142 of the sheath 140 is flush with the lower end face 152 of the tungsten carbide attachment 150, but preferably extends slightly beyond the lower end face 152 of the tungsten carbide attachment 150, for example, by 1-2 mm.
  • the lower end face 142 of the sheath 140 and the lower end face 152 of the tungsten carbide attachment 150 provide an outer annular rotating joint surface and an inner annular rotating joint surface, respectively.
  • the lower end surface 142 of the sheath 140 and the lower end surface 152 of the tungsten steel attachment 150 are respectively formed by The outer annular rotary joint surface and the inner annular rotary joint surface are provided radially separated.
  • the tungsten carbide attachment 150 is attached to and extends to cover the entire lower end face of the impeller hub 110, the outer annular rotation provided by the lower end face 142 of the sheath 140 and the lower end face 152 of the tungsten carbide attachment 150, respectively
  • the engagement surface and the inner annular rotational engagement surface may be continuous.
  • the impeller axial support assembly 200 includes an outer casing 210 adapted to mechanically engage the support assembly 300 (shown only in FIG. 1 ) of the impeller stage 100 , closely surrounding the lower portion of the impeller stage 100 , ie the impeller stage 100 .
  • the inner casing 220 of the sheath 140, the guide vanes 230 spirally extend between the inner casing 220 and the outer casing 230, forming a guide vane channel 225 allowing water to flow therethrough.
  • the guide vane passages 225 of each impeller stage 100 are in fluid communication with the impeller passages 125 and the impeller passages 125 of adjacent impeller stages 100 are in fluid communication with the guide vane passages 225 to enable water to flow from the inlet area of the pump body assembly 20
  • the section enters, flows through each guide vane channel 225 and impeller channel 125 of each impeller stage 100 arranged in series up and down, and flows out through the water outlet section.
  • the middle piece 240 is fixedly attached to the inner housing 220
  • the ceramic support base 250 that directly supports the contact impeller assembly 100 is attached to the middle piece 240 and remains stationary during operation of the centrifugal pump .
  • the intermediate piece 240 and the ceramic support base 250 define shaft holes 242 and 252, respectively, which allow the pump shaft to pass through.
  • the ceramic support 250 includes an upper surface 254 to serve as a stationary engagement surface in contact with the aforementioned outer and inner annular rotational engagement surfaces.
  • the upper surface 254 of the ceramic support base 250 includes an outer annular stationary engagement portion that engages with the lower end surface 142 of the sheath 140 and an inner annular stationary engagement portion that engages with the lower end surface 152 of the tungsten carbide attachment 150 .
  • the outer annular static joint portion and the inner annular static joint portion of the upper surface 254 of the ceramic support base 250 are also discontinuous. However, in other embodiments not shown, they may be consecutive.
  • the lower end face 142 of the sheath 140 and the lower end face 152 of the tungsten carbide attachment 150 engage the upper surface 254 of the ceramic support seat 250 simultaneously, or preferably prior to the lower end face 152 of the tungsten carbide attachment 150 .
  • the radial width T FIG.
  • the contact between the sheath 140 and the ceramic support 250 can be considered It is an annular "line" contact, which causes the high-speed rotating sheath 140 to rapidly wear the upper surface 254 of the ceramic support seat 250, that is, the outer annular static joint portion, so that the inner annular static joint portion and the inner annular portion with the larger radial width are rapidly worn away.
  • a seal is formed between the impeller assembly 100 and the impeller axial support assembly 200 quickly before the contact between the rotating joint surfaces forms the seal.
  • the axial force received by the impeller assembly 100 is all transmitted to the impeller axial support assembly 200, and the lower end surface 152 of the tungsten steel attachment 150 forms a substantially sealed frictional contact with the upper surface 254 of the ceramic support seat 250.
  • the present application forms a notched notch 262 on any one of the end surface 152 and the surface 254 that are engaged with each other, preferably the ceramic upper end surface 254, and the formation of the notch 262 destroys
  • the vacuum formed between the mutually joined surfaces affects the formation of the above-mentioned molecular force, which is more conducive to reducing the resistance that hinders the relative rotation between the two, correspondingly reducing the energy loss, and further improving the efficiency of the centrifugal pump.
  • FIG. 3a-c clearly show the notches 262 formed on the upper surface 254 of the ceramic support 250.
  • FIG. 3a is a perspective view of the ceramic support base 250
  • FIG. 3c is a top view of the ceramic support base 250
  • FIG. 3b is a cross-sectional view along the line X-X of FIG. 3c.
  • a plurality of notches 262 are provided on the upper surface 254 of the ceramic support base 250 along the circumferential direction around the axial direction Z, preferably evenly arranged around the shaft hole 252 .
  • Notches 262 are recessed downwardly from upper surface 254 into the interior of ceramic support 250, extend radially outwardly from the inner peripheral surface defining shaft bore 252, and terminate radially inward of the outer annular stationary engagement portion, or substantially at In the inner annular stationary joint portion which is engaged with the lower end face 152 of the tungsten steel attachment 150 .
  • the number of the notches 262 is not limited to the eight shown in the figure, and may be any number that is evenly arranged along the circumferential direction.
  • the shape of the notch 262 is also not limited to the substantially oval shape shown in the figure.
  • the slot 262 has generally parallel sides 272 , a generally arcuate radially outer end surface 274 and a generally concavely curved bottom surface 276 .
  • the slot 262 may have a circular shape, an oval shape, any polygonal shape, any irregular shape, or a combination of any two or more of the foregoing.
  • the extending direction of the notch 262 is not limited to the radial direction shown in the figure, but can be modified to extend spirally, extend along the circumferential direction, extend obliquely in any direction, extend in a zigzag manner, etc. according to actual needs.
  • the size of the slot 262 can also be set as desired. In the illustrated embodiment, the radial extension of the slot 262 is limited within the inner annular stationary engagement portion.
  • the depth d to which the slot 262 extends into the ceramic support 250 may be between one quarter and one half, preferably about one third, of the overall thickness D of the ceramic support 250 .
  • the present application is not limited to the structure in which the ceramic support base 250 is completely embedded in the concave portion of the middle piece 240 as shown in the figure,
  • the ceramic support base 250 may be partially embedded in the middle piece 240 , or may be attached to the upper surface of the middle piece 240 .
  • the middle piece 240 may be omitted so that the ceramic support base 250 may be directly attached to the inner case 220 .
  • the ceramic support base 250 may be an annular member directly embedded inside the inner casing 220 .
  • ceramic support base 250 and the tungsten steel attachment 150 are not limited to the annular plane structure shown in the figure, but may have any suitable structure, and only need to provide the structure with the hardness, material and size characteristics of the application.
  • An annular rotating or stationary joint surface or joint portion suffices.
  • ceramic support 250 and tungsten carbide attachment 150 may have any other shape or configuration, such as may include hooks or any other engagement features for attachment to inner housing 220 or impeller hub 110 .
  • the way of attaching the sheath 140 made of stainless steel and the tungsten steel attachment 150 made of tungsten steel to the impeller hub 110 and the way of attaching the middle piece 240 and the ceramic support seat 250 to the inner casing 220 can be performed as required Changes are not limited to the details shown.
  • the upper surface 254 of the ceramic support 250 being formed of a ceramic material as shown in engagement with the impeller assembly 100, the upper surface ( If the ceramic support seat 250 is not provided), or use the upward surface of the inner shell 220 (if the middle piece 240 and the ceramic support seat 250 are not provided) to which a certain thickness of ceramic material is applied (eg sprayed)
  • An axial support surface for engagement with the impeller assembly 100 is provided.
  • the stainless steel sheath 140 and the tungsten steel attachment 150 of the impeller assembly 100 can also be omitted, and the lower end face 142 and the lower end face 152 shown in the figure are provided by applying or spraying a coating of the corresponding material to some parts of the impeller hub 110 .
  • the sheath 140 of the impeller assembly 100 is also configured to effectively space the high-speed rotating impeller hub 110 from the inner peripheral surface of the inner casing 220 of the vane cavity assembly 200 surrounding the impeller hub 100 222 ( Figure 2).
  • the length of the sheath 140 extending in the axial direction Z substantially corresponds or approximately corresponds to the axial length of the inner casing 220 along the circumference of the impeller hub 110 .
  • centrifugal pump comprising 5 impeller stages of FIG. 1
  • the present application is by no means limited to centrifugal pumps comprising 5 impeller stages, and the centrifugal pump may include one, two, three, four one, six or more impeller stages.
  • the impeller assembly 100 is engaged with the ceramic support 250 of the impeller axial support assembly 200 via its tungsten steel attachment 150 and stainless steel sheath 140
  • the second shown in Figure 4 The embodiment is different from the first embodiment of FIGS. 1-3c only in that the impeller assembly 100 does not include the stainless steel sheath 140, and the impeller assembly 100 is only engaged with the ceramic support 250 of the impeller axial support assembly 200 via its tungsten steel attachment 150, The purpose of reducing the undesired force between the two can also be achieved.
  • Other structures of the second embodiment shown in FIG. 4 are the same as those of the first embodiment, and will not be repeated here.

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Abstract

一种离心泵，包括：泵轴(11)；叶轮组件(100)，其包括叶轮毂(110)和叶轮(120)，叶轮毂(110)的下端面附接有钨钢附件(150)，所述钨钢附件(150)包括允许泵轴(11)穿过的轴孔和作为旋转接合面的下端面(152)；轴向地支撑叶轮组件(100)并且保持静止的叶轮轴向支撑组件(200，200')，所述叶轮轴向支撑组件(200，200')包括陶瓷支撑件(250)，所述陶瓷支撑件(250)限定出允许泵轴(11)穿过的轴孔(252)，和被构造成在离心泵的操作过程中与所述钨钢附件(150)的下端面(152)摩擦接合使得所述叶轮组件(100)承受的轴向力被传递至所述叶轮轴向支撑组件(200，200')的静止接合面(254)。钨钢附件(150)和陶瓷支撑件(250)的平面接合使得在传递轴向力的情况下两者之间摩擦力最小，减少了能量损失，提高了离心泵的效率。

Description

离心泵
本申请要求下列中国专利申请的优先权，其全部内容通过引用结合在本申请中。
序号 申请日 申请号 名称
1 2021-02-04 202110156817.8 离心泵
2 2021-02-04 202120325349.8 离心泵
技术领域
本申请涉及离心泵技术领域，尤其涉及高转速、高扬程的深井用多级离心泵。
背景技术
深井用离心泵总体上包括电机总成和具有被泵轴驱动而旋转的一个或多个叶轮组件的泵体总成。传统的离心泵的泵轴转速一般在1300rpm左右，若要离心泵输出的水的扬程达到130m，通常离心泵的高度可能达到3m，所以，这种深井泵体积大、非常笨重。
深井用离心泵大多用于农业浇灌，使用环境通常在井下110m-500m不等的深度。在高山等自然环境恶劣的应用中，操作非常不方便。特别是，仅仅对于离心泵的搬运来说，工作人员需要人力抬到山顶，这可能需要几个小时、甚至一天的时间，将庞大、笨重的离心泵安装到几百米深的井底以及后续可能的维修都非常困难。这很大程度上限制了离心泵的应用。
希望能够提高泵的效率，减小泵的体积和重量，以解决或至少部分地改善上述问题。
发明内容
本申请的目的是提供一种新式离心泵结构，其通过减少离心泵内的旋转部件和静止部件之间的摩擦耗能而提高了离心泵的效率，从而大大减小 了泵的体积和重量。
具体地，本申请提供了一种离心泵，包括：
泵轴；
被泵轴驱动而绕轴向方向旋转的叶轮组件，所述叶轮组件包括限定出接合泵轴的轴孔的叶轮毂，和附接到所述叶轮毂并且从叶轮毂的外周面径向向外螺旋形延伸的叶轮，叶轮毂的下端面附接有钨钢附件，所述钨钢附件包括允许泵轴穿过的轴孔和作为旋转接合面的下端面；
轴向地支撑叶轮组件并且保持静止的叶轮轴向支撑组件(200，200′)，所述叶轮轴向支撑组件包括陶瓷支撑件，所述陶瓷支撑件限定出允许泵轴穿过的轴孔，和被构造成在离心泵的操作过程中与所述钨钢附件的下端面摩擦接合使得所述叶轮组件承受的轴向力被传递至所述叶轮轴向支撑组件的静止接合面。
在一个实施例中，所述钨钢附件被嵌置于形成在所述叶轮毂的下端面上的凹口内，或者被附接于所述叶轮毂的下端面。
在一个实施例中，所述静止接合面包括凹陷到所述陶瓷支撑件内的多个槽口，所述槽口从所述陶瓷支撑件的限定轴孔的内表面径向向外突伸。
在一个实施例中，所述多个槽口沿围绕轴向方向的周向方向均匀间隔开布置。
在一个实施例中，所述多个槽口从所述静止接合面凹陷到所述陶瓷支撑件内的深度为所述陶瓷支撑件的轴向厚度的四分之一至二分之一之间。
在一个实施例中，所述离心泵包括多个所述叶轮组件。
在一个实施例中，在所述叶轮组件是离心泵最下方的第一叶轮组件时，所述叶轮轴向支撑组件是进口座支撑组件。
在一个实施例中，在所述叶轮组件是除最下方的第一叶轮组件之外的其它叶轮组件时，所述叶轮轴向支撑组件是导叶腔体组件，所述导叶腔体组件还包括限定出导叶通道的外壳体和内壳体，限定出所述静止接合面的静止支撑件被附接到所述内壳体。
在一个实施例中，所述陶瓷支撑件被直接附接到所述内壳体，或者经由中间件附接到所述内壳体。
在一个实施例中，所述钨钢附接和所述陶瓷支撑件之一或两者是平面 环形部件。
在一个实施例中，所述叶轮从所述叶轮毂的外周面的上部伸出，并且所述叶轮组件还包括围绕着所述叶轮毂的外周面的下部附接的护套，所述护套限定出在轴向方向上与所述钨钢附件的下端面齐平或向下延伸稍超出后者的下端面。
在一个实施例中，所述陶瓷支撑件的静止接合面包括分别与所述钨钢附件的下端面和所述护套的下端面接合的内环形静止接合部分和外环形静止接合部分。
在一个实施例中，凹陷到所述陶瓷支撑件内的多个槽口设置在所述静止接合面的所述内环形静止接合部分内。
在一个实施例中，在垂直于所述轴向方向的横截面中，所述下端面具有在1-5mm之间的径向宽度。
本申请的离心泵包括多个叶轮级组，每一个叶轮级组包括进行高速旋转运动的叶轮组件和对叶轮组件起轴向支撑作用的静止不动的叶轮轴向支撑组件，其中叶轮组件包括钨钢附件，叶轮轴向支撑组件包括陶瓷支撑件，离心泵操作过程中，高速旋转的叶轮组件的钨钢附件的下端面与静止不动的叶轮轴向支撑组件的陶瓷支撑件的上端面摩擦接合，形成平面密封，同时叶轮组件承受的轴向力经由此平面接合传递至静止不动的叶轮轴向支撑组件。钨钢附件和陶瓷支撑件的平面密封接合使得在传递轴向力的情况下两者之间的摩擦力最小，而且在相接合的两个平面之间形成真空的情况下产生的阻碍两者之间相对转动的分子间作用力最小。这减少了因此而造成的能量损失，提高了离心泵的效率。
附图说明
下面将参考附图、结合本申请的示例性实施例详细描述本申请的前述和其它特征、优势和益处。应理解，附图并未按比例绘制，仅仅用于示意本申请的原理，而不意于将本申请限制于图示的详细结构。另外，图中示出的零部件不必须存在本申请的所有实施方式中，图示未示出的零部件有可能存在于本申请的某些实施方式中。
图1是本申请的示例性离心泵的部分分解的立体图，其中重点示意了 离心泵的泵体总成的叶轮级组的布置；
图2示出了在图1的离心泵中被标注出的叶轮级组B3的叶轮组件和叶轮轴向支撑组件的结构细节的剖视图，根据本申请的第一实施例构造；
图3a-3c为图1和2的叶轮轴向支撑组件中的静止支撑件的不同视图；
图4是图2的可替代实施例，根据本申请的第二实施例构造。
具体实施方式
下面参考附图具体描述本申请的离心泵。贯穿各附图，结构或功能相同或相似的部分具有相同的附图标记。
参考图1，本申请的离心泵总体上包括马达总成10和泵体总成20。马达总成10主要包括马达壳体和容置于马达壳体内、能够输出高转速的马达。马达总成10的构造和结构细节不是本申请的重点，为了突出重点，图1中仅示意性示出了马达总成10，并未示出其内部细节。泵体总成20包括泵套筒22和容置于泵套筒22内的至少一个、例如多个叶轮级组。泵轴11从马达总成10内伸出，将马达输出的旋转运动传递至泵体总成20内的各叶轮级组的叶轮组件。泵轴11限定出包括向上方向和向下方向的轴向方向Z。
本申请的离心泵使用时通常竖直放置。所以本申请的描述中使用的方向性术语都以组装在离心泵中后并且竖直放置时的工作状态为参考。例如“上”部或“上”方、或“下”部或“下”方分别指部件在组装到离心泵中之后并且在组装好的离心泵处于竖直工作状态时该部件的上部或上方、或下部和下方。
在轴向方向Z上，从下向上，泵体总成20依次包括：最靠近马达总成10的进水区段，例如，在图1的分解图中，该区段包括泵套筒22的包括进水孔31的进水部段32，容置于泵套筒22的进水部段32内的各部件，包括、但不限于将泵轴11连接到马达输出轴的连接结构等；由多个上下串联布置的叶轮级组B1-B5构成的叶轮区段，例如，在图1的5级示例性离心泵的分解图中，该区段包括泵套筒22的中间部段34，和容置于泵套筒22的中间部段34内的各叶轮级组B1-B5，其中与进水区段相邻的为第一叶轮级组B1，第二至第五叶轮级组B2，B3，B4和B5从下向上依次串联布置；以及位于进水区段相反端的出水区段，例如，在图1的分解图中，该区段包括 泵套筒22的出水部段36，容置于泵套筒22的出水部段36内的各部件，例如出水口腔体组件42，以及图中未示出的可选的单向阀组件等等。
在离心泵操作过程中，马达驱动泵轴11旋转，水经由进水区段的进水孔31进入离心泵内，串联布置的叶轮级组中的叶轮组件高速旋转将水输送至出水区段，经由出水口腔体组件42离开离心泵。
典型地，在如图示的包括多个叶轮级组B1-B5的离心泵中，对于除与进水区段相邻的第一叶轮级组B1之外的其它叶轮级组B2-B5来说，每一个叶轮级组包括被泵轴11驱动而一同旋转的叶轮组件100，环绕着叶轮组件100的下部并且提供轴向支撑作用的导叶腔体组件200，以及环绕着叶轮组件100的上半部并对其提供支撑的支撑体组件300。第一叶轮级组B1、即最下方叶轮级组由于与泵体总成20的进水区段相邻并连接因而具有稍稍不同的结构，该第一叶轮级组B1的叶轮组件100同样包括环绕其上部的支撑体组件300，不同的是，叶轮组件100的下部由结构稍稍不同于上述导叶腔体组件200的进口座组件200′轴向支撑。
对第一叶轮级组B1的叶轮组件100提供轴向支撑的进口座组件200′虽然与对其它叶轮级组B2-B5的叶轮组件100提供轴向支撑的导叶腔体组件200结构不同，但用于第一叶轮级组B1的进口座组件200′和第一叶轮级组B1的叶轮组件100之间的轴向接合和支撑结构与用于其它叶轮级组B2-B5的导叶腔体组件200和它们的叶轮组件100之间的轴向接合和支撑结构是相同的。鉴于此，在本文的描述中，用于第一叶轮级组B1的进口座组件200′和用于其它叶轮级组B2-B5的导叶腔体组件200被统称为“叶轮轴向支撑组件”。本申请的重点即在于每一个叶轮级组B1-B5中高速旋转运动的叶轮组件100与静止不动的叶轮轴向支撑组件200′或200之间的接合结构。
具体来讲，在本申请中，对于每一个叶轮级组B1-B5来说，其在离心泵工作过程中承受的轴向力都经由叶轮轴向支撑组件的轴向支撑而传递至叶轮轴向支撑组件。由此，为了减小在叶轮组件100和其叶轮轴向支撑组件200′或200相摩擦接合的表面之间产生的阻碍两者相对旋转的作用力，进而降低由此带来的能量消耗和效率降低，本申请的叶轮组件100包括钨钢附件，叶轮轴向支撑组件包括与钨钢附件接触接合的陶瓷支撑件。离心 泵操作时，高速旋转运动的叶轮组件和静止不动的叶轮轴向支撑组件通过钨钢附件与陶瓷支撑件的接合或组合实现了接合表面之间的摩擦力最小化，以及接合表面在密封、进而形成真空的情况下两表面间的分子结合力的最小化，由此达到了上述不利作用力的最小化。
下面参考图2-3c详细地描述本申请的第一实施例。
图2的剖视图中示出了图1中标注出的叶轮级组B3中包含的叶轮组件100和叶轮轴向支撑组件、即导叶腔体组件200。本领域内技术人员应理解，在下面描述的叶轮组件100和叶轮轴向支撑组件200之间的支撑和接合结构同样适用于所有其它叶轮级组B1，B2，B4和B5。
叶轮组件100主要包括叶轮毂110、叶轮120和叶轮座130。叶轮毂110呈大致筒形，限定出允许离心泵的泵轴11穿过并与其接合的轴孔112。通常，叶轮毂110与泵轴11可以经由键接合方式相接合，图2中示意性示出了轴孔112中的键槽。
叶轮120从叶轮毂110的外周面114的上部分径向向外并且朝向上端螺旋形延伸。叶轮座130位于叶轮120径向外面并且环绕着叶轮120的外周。叶轮120和叶轮座130之间形成允许水流经的叶轮通道125。在本申请的一个实施例中，叶轮120和叶轮毂110一体地形成，叶轮座130以本领域内任何已知的方式附接于叶轮120的外周以随叶轮120一起旋转。本领域内技术人员可以理解，叶轮毂110、叶轮120和叶轮座130可以分别单独地形成，然后附接到一起，或者其中的至少两者或三者一体地形成。
叶轮毂110的外周面114的下部分附接有护套140，叶轮毂110的下端面附接有钨钢附件150。护套140和钨钢附件150被附接到叶轮毂110的外周面114和下端面的方式可以包括、但不限于过盈配合、利用紧固件连接等本领域内任何已知的连接方式。根据本申请的原理，护套140可以由不锈钢材料形成。在本申请中，在轴向方向上，护套140的下端面142与钨钢附件150的下端面152齐平，但优选稍稍延伸超出钨钢附件150的下端面152，例如超出1-2mm。护套140的下端面142和钨钢附件150的下端面152分别提供外环形旋转接合面和内环形旋转接合面。在如图示钨钢附件150以嵌置方式固持于形成在叶轮毂110的下端面上的凹槽中的实施例中，分别由护套140的下端面142和钨钢附件150的下端面152提供的外环形 旋转接合面和内环形旋转接合面是径向分离开的。然而，可以设想，如果钨钢附件150被附接于并且延伸覆盖叶轮毂110的整个下端面时，则分别由护套140的下端面142和钨钢附件150的下端面152提供的外环形旋转接合面和内环形旋转接合面可以是连续的。
叶轮轴向支撑组件200包括适于与叶轮级组100的支撑件组件300(仅在图1中示出了)机械接合的外壳体210，紧密环绕叶轮级组100的下部、即叶轮级组100的护套140的内壳体220，导叶230在内壳体220和外壳体230之间螺旋形延伸，形成允许水流经的导叶通道225。每一个叶轮级组100的导叶通道225与叶轮通道125流体连通，并且相邻叶轮级组100的叶轮通道125与导叶通道225流体连通，使得水能够从泵体总成20的进水区段进入、流经由上下串联布置的各叶轮级组100的各导叶通道225和叶轮通道125、经由出水区段流出。
在图示实施例中，中间件240被固定地附接于内壳体220，直接支撑接触叶轮组件100的陶瓷支撑座250附接于中间件240上并且在离心泵操作过程中保持静止不动。中间件240和陶瓷支撑座250分别限定出允许泵轴穿过的轴孔242和252。陶瓷支撑座250包括上表面254，以用作与上述外环形旋转接合面和内环形旋转接合面接触的静止接合面。
如图2所示，在叶轮组件100和叶轮轴向支撑组件200的装配状态，护套140的下端面142和钨钢附件150的下端面152均接合陶瓷支撑座250的上表面254，换句话说，陶瓷支撑座250的上表面254包括与护套140的下端面142接合的外环形静止接合部分和与钨钢附件150的下端面152接合的内环形静止接合部分。与外环形旋转接合面和内环形旋转接合面相对应地，陶瓷支撑座250的上表面254的外环形静止接合部分和内环形静止接合部分也是不连续的。然而，在未示出的其他实施例中，它们可以是连续的。
在离心泵操作过程中，护套140的下端面142和钨钢附件150的下端面152同时、或者优选优先于钨钢附件150的下端面152接合陶瓷支撑座250的上表面254。在护套140的径向宽度T(图2)足够小情况下，例如在1-5mm之间、优选在2-4mm、更优选3mm，可以认为护套140与陶瓷支撑座250之间的接触是环形“线”接触，这使得高速旋转的护套140将陶瓷 支撑座250的上表面254、即外环形静止接合部分迅速磨损，从而在径向宽度较大的内环形静止接合部分和内环形旋转接合面之间的接触形成密封之前、在叶轮组件100和叶轮轴向支撑组件200之间迅速形成密封。
随着陶瓷支撑座250的上表面254的外环形静止接合部分被磨损，叶轮组件100的钨钢附件150的下端面152与陶瓷支撑座250的上表面254、具体为内环形静止接合部分之间的接触逐渐紧密，同时叶轮组件100受到的轴向力全部传递至叶轮轴向支撑组件200，钨钢附件150的下端面152与陶瓷支撑座250的上表面254形成实质上密封的摩擦接触。在端面152与表面254形成实质上密封的摩擦接触之后，两表面之间形成真空，形成端面152的钨钢材料和形成表面254的陶瓷材料确保了在此真空密封情况下两者之间的分子结合力尽可能地小，最大程度地降低由此耗费的能量，提高离心泵的效率。
为了更进一步减小、甚至消除此分子结合力的生成，本申请在相互接合的端面152和表面254中任一者、优选陶瓷上端面254上形成缺口式槽口262，槽口262的形成破坏了相互接合的表面之间形成的真空，影响了上述分子力的形成，更加有利于减小阻碍两者之间相对旋转的阻力，相应地减少了能量损失，进一步提高了离心泵的效率。
图3a-c清楚地示出了形成在陶瓷支撑座250的上表面254上的槽口262。其中，图3a为陶瓷支撑座250的立体图，图3c为陶瓷支撑座250的俯视图，图3b为沿图3c的线X-X的剖视图。
从图中可以看出，多个槽口262沿围绕轴向方向Z的周向方向设置于陶瓷支撑座250的上表面254上，优选围绕着轴孔252均匀布置。槽口262从上表面254向下凹陷到陶瓷支撑座250内部，从限定轴孔252的内周面径向向外延伸，终止于外环形静止接合部分径向向内的位置，或者基本上位于与钨钢附件150的下端面152相接合的内环形静止接合部分内。
槽口262的数量不限于图示的8个，可以是沿周向方向均匀布置的任意多个。
槽口262的形状也不限制于图示的大致长圆形。在图示的示例性实施例中，槽口262具有大致平行的侧面272，大致弧形的径向外端面274和大致下凹状的弯曲底表面276。可选地，槽口262可以具有圆形，椭圆形，任 意多边形，任意不规则形状，或者前述中任两意两个或更多个的组合形状。
槽口262的延伸方向也不限于图示的径向方向，而是可以根据实际需要修改为螺旋形延伸、沿周向方向延伸、沿任意方向倾斜延伸、蜿蜒曲折地延伸等。
槽口262的尺寸也可以根据需要进行设置。在图示实施例中，槽口262的径向延伸尺寸被限制于内环形静止接合部分内。槽口262延伸到陶瓷支撑座250内的深度d可以为陶瓷支撑座250总厚度D的四分之一至二分之一之间，优选大约三分之一。
本领域内的技术人员还应了解，在不偏离本申请的原理的情况下，本申请并不限制于如图中所示地陶瓷支撑座250完全嵌置于中间件240的凹部内的结构，陶瓷支撑座250可以部分地嵌置于中间件240内，或者可以附接于中间件240的上表面。可选地，中间件240可以省略，使得陶瓷支撑座250可以直接附接于内壳体220。在一个实施例中，陶瓷支撑座250可以是直接嵌置于内壳体220内部的环形件。
本领域技术人员还应理解，陶瓷支撑座250和钨钢附件150不限于图示的环形平面结构，而是可以才有任何合适的结构，只需提供具有本申请所属硬度、材料和尺寸特征的环形旋转或静止接合面或接合部分即可。例如陶瓷支撑座250和钨钢附件150可以具有任何其它形状或结构，比如可以包括用于附接到内壳体220或叶轮毂110的钩或任何其它接合特征。
如前面所述，不锈钢材料的护套140和钨钢材料的钨钢附件150到叶轮毂110的附接方式以及中间件240和陶瓷支撑座250到内壳体220的附接方式可以根据需要进行改变，不限于图示的细节。
还可以设想，不同于图示的由陶瓷材料形成的陶瓷支撑座250的上表面254与叶轮组件100相接合，可以使用施用(例如喷涂)了一定厚度的陶瓷材料的中间件240的向上表面(如果不设置陶瓷支撑座250的情况下)、或者利用施用(例如喷涂)了一定厚度的陶瓷材料的内壳体220的向上表面(如果不设置中间件240和陶瓷支撑座250的情况下)来提供与叶轮组件100相接合的轴向支撑面。同理，叶轮组件100的不锈钢护套140和钨钢附件150也可以省略，通过向叶轮毂110的某些部分施用或喷涂相应材料的涂层来提供图示的下端面142和下端面152。
在图示的实施例中，叶轮组件100的护套140还配置成有效地间隔开高速旋转的叶轮毂110与导叶腔体组件200的内壳体220的环绕着叶轮毂100的内周面222(图2)。由此，护套140沿轴向方向Z延伸的长度基本上对应于或大致相当于内壳体220沿环绕叶轮毂110的轴向长度。
本申请虽然参考图1的包括5个叶轮级组的离心泵进行了描述，但本申请绝不仅限于包括5个叶轮级组的离心泵，离心泵可以包括可以一个、两个、三个、四个、六个或更多个叶轮级组。
在上面参考图1-3c描述了的第一实施例，叶轮组件100经由其钨钢附件150和不锈钢护套140与叶轮轴向支撑组件200的陶瓷支撑件250接合，图4示出的第二实施例不同于图1-3c的第一实施例仅在于：叶轮组件100不包括不锈钢护套140，叶轮组件100仅经由其钨钢附件150与叶轮轴向支撑组件200的陶瓷支撑件250接合，同样能够实现减小阻碍两者之间不希望的作用力的目的。图4中示出的第二实施例的其它结构与第一实施例相同，这里不再赘述。
尽管在上面参考图中示出的实施例描述了本发明，但是对于本领域的普通技术人员而言显而易见的是，其他实施例和示例可以执行相似的功能和/或获得相似的结果。由此设想所有这样的等效实施例和示例都在本发明的精神和范围之内，并且出于所有目的旨在由以下非限制性的权利要求覆盖。

Claims (14)

  1. 一种离心泵，其特征在于，包括：
    泵轴(11)；
    被泵轴(11)驱动而绕轴向方向(Z)旋转的叶轮组件(100)，所述叶轮组件(110)包括限定出接合泵轴(11)的轴孔(112)的叶轮毂(110)，和附接到所述叶轮毂(110)并且从叶轮毂(110)的外周面(114)径向向外螺旋形延伸的叶轮(120)，叶轮毂(110)的下端面附接有钨钢附件(150)，所述钨钢附件(150)包括允许泵轴(11)穿过的轴孔(154)和作为旋转接合面的下端面(152)；
    轴向地支撑叶轮组件(110)并且保持静止的叶轮轴向支撑组件(200，200′)，所述叶轮轴向支撑组件包括陶瓷支撑件(250)，所述陶瓷支撑件(250)限定出允许泵轴(11)穿过的轴孔(252)，和被构造成在离心泵的操作过程中与所述钨钢附件(150)的下端面(152)摩擦接合使得所述叶轮组件(100)承受的轴向力被传递至所述叶轮轴向支撑组件的静止接合面(254)。
  2. 根据权利要求1所述的离心泵，其特征在于，所述钨钢附件(150)被嵌置于形成在所述叶轮毂(110)的下端面上的凹口内，或者被附接于所述叶轮毂(110)的下端面。
  3. 根据权利要求2所述的离心泵，其特征在于，所述静止接合面(254)包括凹陷到所述陶瓷支撑件(250)内的多个槽口(262)，所述槽口从所述陶瓷支撑件(250)的限定轴孔(252)的内表面径向向外突伸。
  4. 根据权利要求3所述的离心泵，其特征在于，所述多个槽口(262)沿围绕轴向方向(Z)的周向方向均匀间隔开布置。
  5. 根据权利要求3所述的离心泵，其特征在于，所述多个槽口(262)从所述静止接合面凹陷到所述陶瓷支撑件(250)内的深度(d)为所述陶瓷支撑件(250)的轴向厚度(D)的四分之一至二分之一之间。
  6. 根据权利要求1-5中任一项所述的离心泵，其特征在于，所述离心泵包括多个所述叶轮组件。
  7. 根据权利要求6所述的离心泵，其特征在于，在所述叶轮组件是离心泵最下方的第一叶轮组件时，所述叶轮轴向支撑组件是进口座支撑组件(200′)。
  8. 根据权利要求7所述的离心泵，其特征在于，在所述叶轮组件是除最下方的第一叶轮组件之外的其它叶轮组件时，所述叶轮轴向支撑组件是导叶腔体组件(200)，所述导叶腔体组件还包括限定出导叶通道(225)的外壳体(210)和内壳体(220)，限定出所述静止接合面(254)的静止支撑件(250)被附接到所述内壳体(220)。
  9. 根据权利要求8所述的离心泵，其特征在于，所述陶瓷支撑件(250)被直接附接到所述内壳体(220)，或者经由中间件(240)附接到所述内壳体(220)。
  10. 根据权利要求8或9所述的离心泵，其特征在于，所述钨钢附接(150)和所述陶瓷支撑件(250)之一或两者是平面环形部件。
  11. 根据权利要求1-5中任一项所述的离心泵，其特征在于，所述叶轮(120)从所述叶轮毂(100)的外周面(114)的上部伸出，并且所述叶轮组件(100)还包括围绕着所述叶轮毂(100)的外周面(114)的下部附接的护套(140)，所述护套(140)限定出在轴向方向上与所述钨钢附件(150)的下端面(153)齐平或向下延伸稍超出后者的下端面(142)。
  12. 根据权利要求11所述的离心泵，其特征在于，所述陶瓷支撑件(250)的静止接合面(254)包括分别与所述钨钢附件(150)的下端面(153)和所述护套(140)的下端面(142)接合的内环形静止接合部分和外环形静止接合部分。
  13. 根据权利要求12所述的离心泵，其特征在于，凹陷到所述陶瓷支撑件(250)内的多个槽口(262)设置在所述静止接合面(254)的所述内环形静止接合部分内。
  14. 根据权利要求11所述的离心泵，其特征在于，在垂直于所述轴向方向的横截面中，所述下端面(142)具有在1-5mm之间的径向宽度。
PCT/CN2021/117958 2021-02-04 2021-09-13 离心泵 WO2022166204A1 (zh)

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WO2013000033A1 (en) * 2011-06-30 2013-01-03 Weir Minerals (India) Private Limited A centrifugal pump and volute liner
CN207554351U (zh) * 2017-12-08 2018-06-29 江苏长江水泵有限公司 耐磨多级离心泵
CN207762008U (zh) * 2017-12-01 2018-08-24 湖北扬子江泵业有限责任公司 一种离心泵的耐磨叶轮
CN111033054A (zh) * 2017-09-26 2020-04-17 赛莱默欧洲有限公司 具有耐磨环的泵
CN211397914U (zh) * 2019-12-17 2020-09-01 沈阳华大流体科技有限公司 一种两端支撑式单密封多级离心泵

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040091352A1 (en) * 2002-11-08 2004-05-13 Gay Farral D. Attachment of bearing elements by deformation
CN101787983A (zh) * 2010-03-12 2010-07-28 肖琼 一种叶片式泵耐磨叶轮
WO2013000033A1 (en) * 2011-06-30 2013-01-03 Weir Minerals (India) Private Limited A centrifugal pump and volute liner
CN111033054A (zh) * 2017-09-26 2020-04-17 赛莱默欧洲有限公司 具有耐磨环的泵
CN207762008U (zh) * 2017-12-01 2018-08-24 湖北扬子江泵业有限责任公司 一种离心泵的耐磨叶轮
CN207554351U (zh) * 2017-12-08 2018-06-29 江苏长江水泵有限公司 耐磨多级离心泵
CN211397914U (zh) * 2019-12-17 2020-09-01 沈阳华大流体科技有限公司 一种两端支撑式单密封多级离心泵

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