WO2013131351A1 - Pompe submersible multi-étages pour mines - Google Patents

Pompe submersible multi-étages pour mines Download PDF

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Publication number
WO2013131351A1
WO2013131351A1 PCT/CN2012/079137 CN2012079137W WO2013131351A1 WO 2013131351 A1 WO2013131351 A1 WO 2013131351A1 CN 2012079137 W CN2012079137 W CN 2012079137W WO 2013131351 A1 WO2013131351 A1 WO 2013131351A1
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WO
WIPO (PCT)
Prior art keywords
sealing surface
guide vane
inlet
balance drum
pump
Prior art date
Application number
PCT/CN2012/079137
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English (en)
Chinese (zh)
Inventor
陆伟刚
李伟
胡博
李辉
Original Assignee
江苏大学
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.)
Filing date
Publication date
Application filed by 江苏大学 filed Critical 江苏大学
Publication of WO2013131351A1 publication Critical patent/WO2013131351A1/fr

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Classifications

    • 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
    • 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
    • F04D1/063—Multi-stage pumps of the vertically split casing type
    • 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0416—Axial thrust balancing balancing pistons
    • 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/047—Bearings hydrostatic; hydrodynamic

Definitions

  • the invention is a multi-stage submersible pump, in particular, the number of impellers for pumping sandy water in the coal mine is relatively large, the pump head is relatively high, the axial force of the impeller is relatively large, and the balance drum is generally used to balance the axial force.
  • the multi-stage submersible pump belongs to the technical field of general mechanical product manufacturing.
  • the balance drum of the multi-stage submersible pump adopts the radial seal method which cannot be compensated.
  • the prior invention patent "Pump axial force balance device" invented a face-sealed, self-compensating balance drum method, but this invention found in practice that there are still serious technical defects, if not improved, it can not be in multi-grade mine Used in submersible pumps.
  • the technical disadvantage of the multi-stage submersible pump shown in Fig. 1 is that there is no bearing support at the bottom end of the rotating shaft, which causes the impeller ring and the impeller hub to wear and damage quickly in the operation of the sandy liquid, although there are many
  • the bottom end of the rotary shaft of the grade submersible pump is supported by bearings, as shown in Figure 2 of the specification in ZL201020548965.1, but because the lubricating fluid of the bottom end bearing has a relatively large sand content, the bearing life is relatively short, and it is also a Technical flaws.
  • the invention provides an innovative design multi-stage submersible pump, wherein the balanced axial force balance drum adopts an end face sealing method capable of automatically compensating, overcomes the defect of the radial sealing type wear failure, and the bottom end of the rotating shaft is increased.
  • the bearing is supported, and the material is lubricated locally, and the bearing water with less sand is used to lubricate the bearing, which overcomes the defect of the sliding bearing wear failure.
  • the basic structure is the same as the existing multi-stage submersible pump in the coal mine.
  • the electric motor and the water pump are coaxial, and the electric motor can work in diving.
  • the water pump is a multi-stage centrifugal pump with a lift of more than 300 meters.
  • the main innovations are:
  • the balance drum that balances the axial force of the rotor adopts an end face sealing method capable of automatic compensation, and the static ring as the balance drum main body can move axially, so that the static ring that does not rotate and the moving ring that rotates synchronously with the rotating shaft are always close together.
  • the end face seal is composed of a main sealing surface and a secondary sealing surface.
  • the outer diameter of the main sealing surface is larger than the diameter of the balance drum, the inner diameter of the main sealing surface is smaller than the diameter of the balance drum, and the dynamic ring sealing surface and the static ring sealing surface of the main sealing surface are fitted.
  • the secondary sealing surface is on the outer side of the main sealing surface, and there is a gap between the moving ring sealing surface of the secondary sealing surface and the static ring sealing surface, and the gap of the secondary sealing surface is between 0.2 mm and 2 mm.
  • the end face seal balance drum is the same as the radial seal balance drum. There is a cylinder blocking high pressure zone and low pressure zone. The diameter of this cylinder is called balance drum diameter. The balance drum diameter determines the axial force balance. The difference is that the main body of the radial seal balance drum rotates synchronously with the rotating shaft, and it relies on the radial gap between the non-rotating final pump body to realize the dynamic and static transition. This gap will wear more, so the leakage is very high. Big.
  • the end face seal balance drum relies on the end face friction of the moving ring and the static ring to realize the dynamic and static transition.
  • the static ring is not rotated as the balance drum main body, and there is a static ring O-ring at the balance drum diameter to ensure that there is no leakage and balance.
  • the other half of the drum rotates synchronously with the rotating shaft, and the sealing gap between the moving ring and the stationary ring is almost equal to zero, so the leakage amount is small.
  • the static ring can also move axially, so that the sealing surface of the moving ring and the static ring continue to be attached together, which is the automatic compensation function of the end face sealing balance drum.
  • the superiority of the face seal balance drum was discovered in the 1980s. Although it has not been used in multi-stage submersible pumps, it has been used as a patent for invention (ZL87100241) in a submersible pump for wells.
  • the seal balance drum has only the primary sealing surface and no secondary sealing surface of the present invention that increases outside the primary sealing surface.
  • the end face seal balance drum without the secondary sealing surface is difficult to design.
  • the specific pressure of the sealing surface is not too large.
  • the sealing surface is damaged.
  • the specific pressure of the sealing surface is too small. In operation, the sealing surface is pushed away by the high pressure liquid, and once pushed, once pushed When opened, it will cause a lot of leakage and completely defeat the balance drum. This defect has caused the ZL87100241 to be unpromoted.
  • the present invention with the addition of a secondary sealing surface effectively overcomes this drawback. Since the end face seal balance drum can balance the axial force in the case of a small amount of leakage, the specific pressure of the seal face should be relatively small compared with the general mechanical seal, which can greatly extend the life of the main seal face. However, a small amount of leakage on the main sealing surface increases the pushing force on the main sealing surface. When the instability of the pump working condition leads to an increase in the leakage amount, the pushing force on the sealing surface increases, and the pushing force increases. This will increase the amount of leakage, and the vicious cycle of pushing force and leakage will cause the main sealing surface to be pushed away by the high pressure liquid.
  • the pressing force of the auxiliary sealing surface can be increased when the leakage of the main sealing surface increases, and the reasonable design can increase the leakage force, and the pressing force of the auxiliary sealing surface increases more than the main sealing.
  • the amount of pushing force is increased to prevent the sealing surface from being pushed away.
  • the clearance of the secondary sealing surface should not be too large or too small. If it is larger than 2mm, the sensitivity is too low, and the pressing force adjustment effect of the secondary sealing surface will be lost. If it is less than 0.2mm, the service life will be affected. When the main sealing surface is worn, The pressure will be too large and the end face seal balance drum will wear out quickly.
  • the lower part of the water pump has a bearing seat including a water inlet guide vane and a liquid storage chamber, and a sliding bearing for supporting the bottom end of the rotating shaft.
  • the lubricating fluid of the sliding bearing is derived from the liquid storage chamber at the lower part of the bearing housing, and the liquid
  • the liquid in the storage chamber is derived from the liquid having a relatively small amount of sand in the upper portion of the inlet guide vane, and the inlet inlet window and the liquid storage chamber in the upper portion of the inlet guide vane are communicated through the axial through hole of the inlet guide vane.
  • Multi-stage submersible pumps have more impeller stages and longer pump shafts.
  • sliding bearings are needed to assist the rotor.
  • the existing multi-stage submersible pumps mostly rely on the impeller ring and the impeller hub as sliding bearings to support the rotor.
  • the materials in these two places are generally not suitable for use as bearings, and the diameters of the two places are relatively large, the line speed is relatively high, and it is easy to wear and damage when running in the sandy water of the mine.
  • ZL201020548965.1 proposes to install a three-composite radial sliding bearing on the bottom end of the rotating shaft, but the bottom end of the rotating shaft is the place with the largest amount of sand, and even the hard alloy is easy to wear and damage.
  • the disclosed invention patent application "a hard alloy sliding bearing water-cooling cooling lubrication system for a submersible pump” (201010591094.6) proposes a sliding bearing for lubricating the bottom end of the rotating shaft at the surface of the pool, which can solve the problem, but is implemented too Complex, packaging, transportation and installation add to the trouble for users.
  • the invention skillfully utilizes the place where the flow rate of the liquid in the guide vane is relatively low, the hard sand is easy to settle in the lower part, and the liquid with less sand content in the upper part of the guide vane is first introduced into the liquid storage chamber, and then a part of the sediment is precipitated. At the bottom of the storage chamber, the liquid at the bottom end of the lubricating bearing is less contained, which ensures a greatly improved service life of the bearing.
  • Another innovation of the present invention is that the inlet angle of the inlet guide vane of the lower portion of the water pump is 90 degrees, and the inlet angle of the inlet guide vane is 10 degrees to 20 degrees.
  • the lower part of the pump of the multi-stage submersible pump has a bearing seat including the inlet guide vane.
  • the inlet angle of the inlet guide vane is 90 degrees
  • the overflow area of the vane inlet is Larger, lower flow rate, sand in sandy water is easy to precipitate
  • the inlet angle of the inlet guide vane is 10 degrees to 20 degrees, which can make the flow of the impeller inlet have a peripheral speed, which can reduce the multi-stage submersible pump.
  • Power under high flow conditions Since the majority of multi-stage submersible pumps are low-ratio centrifugal pumps, reducing the power under high-flow conditions is to reduce their maximum power, thus ensuring safe operation of multi-stage submersible pumps under full lift conditions.
  • the invention has the beneficial effects of overcoming the defects of the existing multi-stage submersible pump, and manufacturing a multi-stage submersible pump with reliable axial force balance device, long end bearing life and relatively small power extreme value with low additional cost. Therefore, the multi-stage submersible pump of the present invention is more competitive in the market.
  • Figure 1 is a simplified diagram of a prior art multi-stage submersible pump.
  • Figure 2 is a schematic diagram of a multi-stage submersible pump embodying the present invention.
  • Fig. 3 is a schematic enlarged view of the end face seal balance drum of Fig. 2.
  • Figure 4 is a two view of the stationary ring of Figure 3.
  • Figure 5 is a two-view view of a static ring of a conventional end face seal balancing drum (without a secondary sealing surface).
  • Figure 6 is a second elevational view of the bearing housing of Figure 2 including the inlet guide vanes.
  • the embodiment of the invention shown in FIG. 2 is a BQW10-300/5-37 multi-stage submersible pump.
  • the basic structure is the same as the existing multi-stage submersible pump in the coal mine.
  • the electric motor and the water pump are coaxial, and the electric motor can dive.
  • the pump is a multi-stage centrifugal pump with a 5-stage impeller and a head of 300 meters. It is different from the existing multi-stage submersible pump.
  • the main innovation is that the balance drum that balances the axial force of the rotor adopts an end face seal that can be automatically compensated. the way.
  • the end face seal is composed of a main sealing surface 9 and a secondary sealing surface 27, the outer sealing surface outer diameter 25 is larger than the balance drum diameter 4, the main sealing surface inner diameter 24 is smaller than the balance drum diameter 4, and the main sealing surface 9 is moving ring
  • the secondary sealing surface 27 is outside the main sealing surface 9
  • the moving ring sealing surface of the secondary sealing surface 27 and the stationary ring sealing surface have a gap
  • the secondary sealing surface gap 22 Between 0.2mm ⁇ 2mm.
  • the face seal balance drum is the same as the radial seal balance drum.
  • the pressure difference is balanced by the pressure difference between the two end faces of a cylinder.
  • the diameter of this cylinder is called the balance drum diameter 4, and the balance drum diameter 4 determines the size.
  • the amount of axial force balance no matter which balance drum can not fully balance the axial force, requires the radial thrust ball bearing 28 to bear the remaining axial force.
  • the pressure in the high pressure zone is determined by the pump head, and the pressure in the low pressure zone is the atmospheric pressure or water level pressure of the inlet.
  • the pressure at the lower end of the end face seal balance drum and the pressure on the outside side are equal to the pressure in the high pressure zone, and the pressure at the upper end of the end face seal balance drum and the pressure on the inner side pass through the static ring pressure relief groove 7, the low pressure chamber 1 and the final stage pump body pressure relief hole 21
  • the pool connection is equal to the pressure in the low pressure zone, which is also substantially the same as the radial seal balance drum.
  • the end face seal balance drum is different from the radial seal balance drum in that the main body of the radial seal balance drum rotates synchronously with the rotary shaft 20, and it relies on the radial gap 23 between the non-rotating final stage pump body 2 to realize the movement and static In the transition, this gap will wear more, so the amount of leakage is large.
  • the end face seal balance drum relies on the end face friction of the moving ring 10 and the static ring 8 to realize the dynamic and static transition, and the static ring 8 as the end face seal balances the drum main body to be non-rotating, and has a static ring O-ring 6 at its balance drum diameter 4.
  • the static ring 8 can also move axially, so that the sealing surface of the moving ring 10 and the static ring 8 continue to be attached together, which is the automatic compensation function of the end face sealing balance drum, preventing the static ring 8 from rotating.
  • the ring stop pin 3 does not prevent the axial movement of the stationary ring 8, and the static ring spring 5 ensures that the sealing surface of the moving ring 10 and the stationary ring 8 can be brought together without a pressure difference.
  • the superiority of the face seal balance drum was discovered in the 1980s. Although it has not been used in multi-stage submersible pumps, it has been used as a patent for invention (ZL87100241) in a submersible pump for wells.
  • the seal balance drum has only the primary seal face 9 and no secondary seal face 27 of the present invention that increases outside the primary seal face.
  • the end face seal balance drum without the secondary sealing surface 27 is difficult to design as shown in Fig. 5.
  • the specific pressure of the sealing surface is not too large, the sealing surface is damaged, the specific pressure of the sealing surface is too small, and the sealing surface is high pressure during operation.
  • the liquid pushes open, and once pushed open, it causes a large amount of leakage and completely defeats the balance drum. This defect has caused the ZL87100241 to be unpromoted.
  • the present invention in which the secondary sealing surface 27 is added effectively overcomes this drawback. Since the end face seal balance drum can balance the axial force in the case of a small amount of leakage, the specific pressure of the seal face should be relatively small compared with the general mechanical seal, which can greatly extend the life of the main seal face 9. However, a small amount of leakage of the main sealing surface 9 increases the pushing force on the main sealing surface 9. When the instability of the pump operating condition causes an increase in the leakage amount, the pushing force on the sealing surface increases, and the pushing force increases. With the vicious cycle of leakage, the main sealing surface 9 is inevitably pushed away by the high pressure liquid.
  • the balance drum diameter 4 of the embodiment is 80 mm
  • the outer diameter 25 of the main sealing surface is 88 mm
  • the inner diameter 24 of the main sealing surface is 72 mm
  • the outer diameter 26 of the secondary sealing surface is 110 mm
  • the main sealing surface 9 does not leak at all, and the dynamic reversal coefficient is 0.5, the force on the main sealing surface 9 is 25 kg, the specific pressure is 1.25 kg/cm 2 , obviously the specific pressure is small, the main sealing surface 9 is not easy to damage.
  • the spring pressure is 10 kg
  • the main sealing surface 9 has a small amount of leakage, and the dynamic reaction coefficient reaches 0.54, the force on the main sealing surface 9 is 0.95 kg, and the specific pressure is 0.05 kg/cm 2 .
  • the main sealing surface 9 has May maintain a fit.
  • the force on the main sealing surface 9 is a negative value, that is, the pushing force is greater than the pressing force, and the main sealing surface 9 is Will be pushed open, this is the flaw of ZL87100241.
  • the secondary sealing surface 27 of the present invention this problem is solved.
  • the primary sealing surface 9 leaks, the pressure on the secondary sealing surface 27 is lowered, and the pressing force is increased, assuming that the primary sealing surface 9 There is a small amount of leakage, and the dynamic reversal coefficient reaches 0.6.
  • the dynamic inverse coefficient on the secondary sealing surface 27 will be less than 1 but greater than the dynamic inverse coefficient of the main sealing surface 9 of 0.6, assuming that the integrated dynamic inverse coefficient on the sealing surface is 0.7, the sealing surface
  • the upper force is 212kg and the specific pressure is 3.9kg/cm 2 , which ensures that the sealing surface is not pushed away further, and because the force of the sealing surface acts on the leaking liquid at this time, as long as the leakage liquid contains The amount of sand is small, and the life of the sealing surface will still be relatively long.
  • the leakage gap of the end face seal is much smaller than the radial gap 23 of the radial seal and the automatic compensation capability of the end face seal balance drum, the leakage amount is much smaller than that of the radial seal balance drum, so the sand passes from the low point to the final stage impeller. The sealing surface of the back blade 12 to the upper portion is difficult.
  • the pressure on the secondary sealing surface 27 is equal to the pressure acting on the balancing drum, that is, the reverse The coefficient is equal to 1, so the specific pressure acting on the main sealing surface 9 is still 1.25 kg/cm 2 .
  • the lower portion of the water pump has a bearing housing 14 including a water inlet guide vane 17 and a liquid storage chamber 13, a sliding bearing 18 for supporting the bottom end 19 of the rotating shaft, and lubrication of the sliding bearing 18.
  • the liquid is derived from the liquid storage chamber 13 in the lower part of the bearing housing 14.
  • the liquid in the liquid storage chamber 13 is derived from the liquid having a relatively small amount of sand in the upper portion of the inlet guide vane 17, that is, the inlet inlet inlet window 17 has a vane inlet window 16 and a liquid.
  • the storage chambers 13 communicate with each other through the inlet guide vanes of the water guide vanes.
  • Multi-stage submersible pumps have more impeller stages and longer pump shafts. Generally, sliding bearings are needed to assist the rotor.
  • the multi-stage submersible pump like Figure 1 relies on the impeller ring and the impeller hub as sliding bearings to support the rotor. It is very easy to wear and damage.
  • ZL201020548965.1 proposes to install a three-composite radial sliding bearing on the bottom end of the rotating shaft, but the bottom end 19 of the rotating shaft is the place with the largest amount of sand, and even the hard alloy is easy to wear and damage.
  • the disclosed invention patent application "a hard alloy sliding bearing water-cooling cooling lubrication system for a submersible pump” (201010591094.6) proposes a sliding bearing for lubricating the bottom end of the rotating shaft at the surface of the pool, which can solve the problem, but is implemented too Complex, packaging, transportation and installation add to the trouble for users.
  • the invention skillfully utilizes the place where the flow rate of the liquid in the guide vane is relatively low, the hard sand is easy to settle in the lower part, and the liquid with less sand content in the upper part of the guide vane is first introduced into the liquid storage chamber 13, and then a part of the sediment is introduced. Precipitated at the bottom of the storage chamber, so that the liquid at the bottom end of the lubrication bearing is less, which ensures that the service life of the bearing is greatly extended.
  • FIG. 2 Another innovation of the embodiment of the present invention shown in Fig. 2 is that the inlet angle 31 of the inlet guide vane of the lower portion of the water pump is 90 degrees, and the inlet angle 30 of the inlet guide vane is 10 degrees to 20 degrees.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne une pompe submersible multi-étages pour mines, caractérisée en ce qu'un moteur électrique est coaxial à une pompe à eau et en ce que le moteur électrique peut fonctionner en immersion. La pompe à eau est une pompe centrifuge multi-étages et la hauteur de relevage est supérieure à 300 mètres. Le piston d'équilibrage de la pompe à eau, qui équilibre la force axiale, utilise un procédé d'étanchéité de face terminale capable de réaliser une compensation automatique, surmontant les inconvénients d'une rupture par usure du procédé d'étanchéité radiale. Un soutien par palier (18) est ajouté à l'extrémité inférieure d'un arbre rotatif (20) et l'utilisation d'eau de la mine contenant relativement peu de vase pour lubrifier le palier surmonte les inconvénients d'une rupture par usure d'un palier glissant.
PCT/CN2012/079137 2012-03-09 2012-07-25 Pompe submersible multi-étages pour mines WO2013131351A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201220108937 2012-03-09
CN201220108937.7 2012-03-09

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WO2013131351A1 true WO2013131351A1 (fr) 2013-09-12

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107218095A (zh) * 2017-05-16 2017-09-29 大连深蓝泵业有限公司 液化天然气降压工况用lng液力透平的轴向力平衡系统
CN109386473A (zh) * 2017-08-14 2019-02-26 山东安立泰泵业股份有限公司 一种轴向力平衡的多级排水泵
CN110439845A (zh) * 2019-08-09 2019-11-12 浙江绿美泵业有限公司 一种低水位单口双吸自平衡潜水泵
CN113530837A (zh) * 2021-07-10 2021-10-22 绍兴市雪花机电有限公司 一种浸入式多段泵及其使用方法
CN118855716A (zh) * 2024-09-29 2024-10-29 浙江登丰泵业有限公司 一种高效能多级密封离心泵

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Publication number Priority date Publication date Assignee Title
JPH09228987A (ja) * 1996-02-26 1997-09-02 Ebara Corp 軸スラスト力バランス機構を具備したポンプ
JPH1182364A (ja) * 1997-09-02 1999-03-26 Mitsubishi Heavy Ind Ltd 多段遠心ポンプ
CN2563342Y (zh) * 2002-06-26 2003-07-30 张波 一种矿用自吸泵
CN1815039A (zh) * 2006-03-03 2006-08-09 江苏大学 一种叶轮自身平衡轴向力的多级离心泵
CN202047989U (zh) * 2010-12-29 2011-11-23 荆锁祥 节段对置双蜗壳矿用耐磨多级泵
CN102705247A (zh) * 2012-03-09 2012-10-03 江苏大学 一种多级矿潜泵

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09228987A (ja) * 1996-02-26 1997-09-02 Ebara Corp 軸スラスト力バランス機構を具備したポンプ
JPH1182364A (ja) * 1997-09-02 1999-03-26 Mitsubishi Heavy Ind Ltd 多段遠心ポンプ
CN2563342Y (zh) * 2002-06-26 2003-07-30 张波 一种矿用自吸泵
CN1815039A (zh) * 2006-03-03 2006-08-09 江苏大学 一种叶轮自身平衡轴向力的多级离心泵
CN202047989U (zh) * 2010-12-29 2011-11-23 荆锁祥 节段对置双蜗壳矿用耐磨多级泵
CN102705247A (zh) * 2012-03-09 2012-10-03 江苏大学 一种多级矿潜泵

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107218095A (zh) * 2017-05-16 2017-09-29 大连深蓝泵业有限公司 液化天然气降压工况用lng液力透平的轴向力平衡系统
CN107218095B (zh) * 2017-05-16 2023-08-08 大连深蓝泵业有限公司 液化天然气降压工况用lng液力透平的轴向力平衡系统
CN109386473A (zh) * 2017-08-14 2019-02-26 山东安立泰泵业股份有限公司 一种轴向力平衡的多级排水泵
CN110439845A (zh) * 2019-08-09 2019-11-12 浙江绿美泵业有限公司 一种低水位单口双吸自平衡潜水泵
CN113530837A (zh) * 2021-07-10 2021-10-22 绍兴市雪花机电有限公司 一种浸入式多段泵及其使用方法
CN118855716A (zh) * 2024-09-29 2024-10-29 浙江登丰泵业有限公司 一种高效能多级密封离心泵
CN118855716B (zh) * 2024-09-29 2025-01-24 浙江登丰泵业有限公司 一种高效能多级密封离心泵

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