WO2016009977A1 - Pompe à arbre vertical - Google Patents

Pompe à arbre vertical Download PDF

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Publication number
WO2016009977A1
WO2016009977A1 PCT/JP2015/069985 JP2015069985W WO2016009977A1 WO 2016009977 A1 WO2016009977 A1 WO 2016009977A1 JP 2015069985 W JP2015069985 W JP 2015069985W WO 2016009977 A1 WO2016009977 A1 WO 2016009977A1
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WO
WIPO (PCT)
Prior art keywords
bearing
rotating shaft
pump
impeller
sleeve
Prior art date
Application number
PCT/JP2015/069985
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English (en)
Japanese (ja)
Inventor
裕輔 渡邊
正治 石井
和彦 杉山
雄二 中塩
内田　義弘
Original Assignee
株式会社荏原製作所
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 株式会社荏原製作所 filed Critical 株式会社荏原製作所
Priority to SG11201610976PA priority Critical patent/SG11201610976PA/en
Priority to CN201580038340.6A priority patent/CN106662109B/zh
Publication of WO2016009977A1 publication Critical patent/WO2016009977A1/fr

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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
    • F04D11/00—Other rotary non-positive-displacement pumps
    • 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
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • 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
    • F04D29/60—Mounting; Assembling; Disassembling

Definitions

  • the present invention relates to a vertical pump that pumps liquids such as river water and drainage, and more particularly to a vertical pump that can improve the durability and maintenance of a bearing that supports a rotating shaft and can easily replace the bearing.
  • FIG. 1 is a schematic diagram showing a conventional vertical shaft pump.
  • a vertical shaft pump has a pump base 514, and the pump base 514 is installed on a pump installation floor 500 at the upper part of a water tank.
  • a guide casing 506 that houses the impeller 504 is suspended from the pump installation floor 500 via the suspension pipe 502.
  • the impeller 504 is fixed to a rotating shaft 509, and the rotating shaft 509 is rotatably supported by an outer bearing 510 and an underwater bearing 508.
  • the method 2) it is possible to appropriately measure or detect the wear state of the underwater bearing 508, and it is also possible to replace the underwater bearing 508. For this reason, in order to confirm the wear of the submerged bearing 508 of the vertical shaft pump, the method 2) has been conventionally performed.
  • the above method 2) is expensive and requires a long time for inspection and maintenance.
  • a vertical shaft pump is lifted using an overhead crane, a mechanical engineer, an operator, a crane operator, and the like who are inspectors are required, and considerable work costs are required for lifting.
  • lifting and reassembling a heavy pump can be a dangerous operation.
  • the lifting and inspection work requires inspection and maintenance after the lifting, and then undergoes the steps of re-installation, centering, and trial operation, which requires a considerable number of days.
  • Patent Document 3 there has been proposed a vertical shaft pump having a structure in which a rotating shaft is supported by two of an underwater bearing disposed below an impeller and an outer bearing above a pump installation floor. According to this structure, since the underwater bearing is located below the impeller (suction side), the wear state of the underwater bearing can be visually inspected from the suction port, and the underwater bearing can be easily replaced. Can do.
  • the present invention has been made in view of such problems of the prior art. Even in a large-capacity pump, the submersible bearing can be easily replaced with the pump installed without pulling up the pump.
  • An object of the present invention is to provide a vertical shaft pump with improved reliability of the underwater bearing.
  • a vertical shaft pump includes an impeller, a rotating shaft that extends through the impeller and to which the impeller is fixed, an outer bearing that supports the rotating shaft, and an impeller A bearing unit that is provided below and supports the rotating shaft that passes through the impeller, and the rotating shaft passes through the impeller from the outer bearing without a bearing other than the outer bearing.
  • the bearing unit includes a first bearing that supports the sliding portion of the rotating shaft on a bearing inner peripheral surface, and a second bearing that supports the sliding portion of the rotating shaft on a bearing outer peripheral surface.
  • the bearing unit is removably attached to the lower side of the impeller.
  • the first bearing and the second bearing are configured to be detachable below the impeller. Is done.
  • the vertical pump according to the fourth aspect of the present invention in the vertical pump according to any one of the first to third aspects, it has a protective cover provided below the bearing unit, and the protective cover includes the bearing There is a small side-facing hole to guide the water flow to the unit.
  • the first bearing and the second bearing are made of the same material,
  • the material is composed of a resin or a resin composite material.
  • the vertical shaft pump extends from the outer bearing through the impeller without any bearing other than the outer bearing, and the bearing receives the rotating shaft below the impeller.
  • the bearing unit includes a first bearing that supports the sliding portion of the rotating shaft on the bearing inner peripheral surface, and a second bearing that supports the sliding portion of the rotating shaft on the outer peripheral surface of the bearing.
  • FIG. 1 It is a schematic diagram which shows the conventional vertical shaft pump. It is a schematic diagram which shows the vertical shaft pump in one Embodiment of this invention. It is a longitudinal cross-sectional schematic diagram explaining the principle of a bearing unit. It is sectional drawing in the XX 'cross section shown in FIG. It is a figure which shows operation
  • upper means the upper side (discharge side) in the state where the vertical shaft pump is installed
  • lower means the lower side (suction side) in the state where the vertical axis pump is installed.
  • FIG. 2 is a schematic diagram showing a vertical shaft pump according to an embodiment of the present invention.
  • the vertical pump is connected to a guide casing 1 having a suction bell mouth 1a and a discharge bowl 1b, a suspension pipe 3 for suspending the guide casing 1 in a water tank 5, and an upper end of the suspension pipe 3
  • the discharge curved pipe 4, the impeller 10 accommodated in the guide casing 1, and the rotating shaft 6 to which the impeller 10 is fixed are provided.
  • the suspension pipe 3 extends downward through an insertion hole 24 formed in the pump installation floor 22 above the water tank 5 and is fixed to the pump installation floor 22 via a pump base 23 provided at the upper end of the suspension pipe 3.
  • the rotating shaft (vertical shaft) 6 extends in the vertical direction through the discharge bent tube 4 and the suspension tube 3, and the lower end thereof is located in the guide casing 1.
  • a pump casing 2 is constituted by the guide casing 1 and the suspension pipe 3.
  • the upper floor F that is an area above the pump installation floor 22 is an area that can be inspected at all times, and the water tank section U that is an area below the pump installation floor 22 is an area that is submerged.
  • the suction bell mouth 1a has an opening on the lower side (suction side), and the upper end of the suction bell mouth 1a is fixed to the lower end of the discharge bowl 1b.
  • the impeller 10 is fixed to the lower part of the rotating shaft 6, and the impeller 10 and the rotating shaft 6 rotate integrally.
  • the impeller 10 has a plurality of blades, and a plurality of guide vanes 14 are disposed above (the discharge side) the impeller 10. These guide vanes 14 are fixed to the inner peripheral surface of the guide casing 1 and the outer peripheral surface of the bowl bush 13.
  • the rotating shaft 6 is rotatably supported by the underwater bearing unit 12 and the outer bearing 11.
  • the underwater bearing unit 12 is located below (the suction side) of the impeller 10 and supports the lower end of the rotating shaft 6.
  • the underwater bearing unit 12 is supported by a support member 15 fixed to the inner peripheral surface of the suction bell mouth 1a.
  • the underwater bearing is not arranged between the outer bearing 11 and the underwater bearing unit 12 including the inside of the bowl bush 13.
  • the outer bearing 11 is provided on the upper part (outside) of the discharge curved pipe 4 and supports the upper part (one end) of the rotating shaft 6.
  • the rotating shaft 6 extends through the impeller 10 from the outer bearing 11 without any bearing other than the outer bearing 11.
  • the underwater bearing unit 12 is disposed on the radially outer side of the rotating shaft 6 (around the rotating shaft 6), and is an inscribed bearing (first bearing) that supports the sliding portion of the rotating shaft 6 on the bearing inner peripheral surface. And a circumscribed bearing (second bearing) that is disposed on the radially inner side of the rotating shaft 6 and supports the sliding portion of the rotating shaft 6 on the outer peripheral surface of the bearing.
  • the first bearing and the second bearing provided in the underwater bearing unit 12 are so-called slide bearings that support the rotating shaft while slidingly contacting the rotating shaft 6 during steady operation of the pump.
  • the outer bearing 11 is configured not only to receive a radial load but also to receive a thrust load.
  • the outer bearing 11 may be a single bearing capable of receiving both a radial load and a thrust load, or a combination of a radial bearing capable of receiving a radial load and a thrust bearing capable of receiving a thrust load. There may be.
  • the rotating shaft 6 protrudes upward from the discharge curved pipe 4.
  • the upper end of the rotary shaft 6 is connected to the drive shaft 42 of the speed reducer 41 via a universal shaft joint 45.
  • the speed reducer 41 is connected to a drive source 43.
  • a diesel engine, a gas turbine, a motor, or the like can be used. Note that the speed reducer 41 may not be used.
  • the submersible bearing 508 is housed in the bowl bush, it is difficult to replace the submersible bearing 508 with the vertical pump installed.
  • the underwater bearing unit 12 is disposed below the impeller 10, if water inside the water tank 5 is removed and an operator enters the lower part of the vertical shaft pump, The amount of wear and damage of the bearing unit 12 can be easily determined, and the underwater bearing unit 12 can be easily replaced.
  • the submersible bearing unit 12 can be inspected and replaced without lifting the vertical shaft pump, the cost required for lifting the vertical shaft pump can be reduced, and the downtime during inspection and replacement can be greatly increased. Can be shortened. Therefore, the economical efficiency and reliability of the pump station can be improved. Moreover, since the position of the underwater bearing unit 12 is lower than the conventional position and is located below the impeller 10, the underwater bearing unit 12 can be surely submerged during the operation of the pump. Therefore, the water film formed between the underwater bearing unit 12 and the rotating shaft 6 can suppress wear of the underwater bearing unit 12 and improve the durability of the underwater bearing unit 12.
  • FIG. 3 is a schematic longitudinal sectional view illustrating the principle of the bearing unit.
  • This bearing unit has a sleeve 31 on the outer periphery of the rotary shaft 30.
  • the material of the sleeve 31 is practically made of cemented carbide or stainless steel.
  • a hollow cylindrical first slide bearing 44 is provided on the outer peripheral side of the sleeve 31. That is, the sleeve 31 contacts and slides inside the first slide bearing 44.
  • the material of the first plain bearing 44 is practically made of a resin material, ceramics, sintered metal, or surface-modified metal.
  • the outer peripheral surface (first sliding portion 46) of the sleeve 31 faces the inner peripheral surface (slip surface) of the first slide bearing 44 through a very narrow first clearance 47, and the first slide bearing. It is configured to slide with respect to 44 sliding surfaces.
  • the outer peripheral portion of the first plain bearing 44 is fixed to the inner peripheral surface of the substantially cylindrical bearing case 32.
  • the material of the bearing case 32 is practically made of metal or resin.
  • a hollow cylindrical second sliding bearing 39 is provided on the outer peripheral surface of the bearing case 32.
  • the material of the second plain bearing 39 is practically made of a resin material, ceramics, sintered metal, or surface-modified metal.
  • a substantially cylindrical sleeve case 38 is fixed to the rotating shaft 30 by fixing means 33a such as a fixing pin or a bolt, and the sleeve case 38 rotates with the rotating shaft 30 as the rotating shaft 30 rotates. It is configured.
  • a sleeve 37 is provided on the inner peripheral surface of the sleeve case 38, and the inner peripheral surface (second sliding portion 36) of the sleeve 37 is the second narrower than the outer peripheral surface (sliding surface) of the second slide bearing 39.
  • the sleeves 31 and 37 are generally installed on the outer periphery of a shaft member or the like, but in the present application, in order to make the configuration of the bearing unit easy to understand, for the sake of convenience, the sleeves 31 and 37 bear the main bearing material.
  • First and second sliding bearings are used, and the opposed sliding members are referred to as sleeves.
  • the above is the configuration of the bearing unit.
  • the bearing unit is fixed to a support member 35 or the like connected to a casing such as a pump via a flange portion 32a of the bearing case 32 by fixing means 33b such as a bolt.
  • the sleeve 31 is held on the outer periphery of the rotating body (rotating shaft 30), and the non-rotating slide bearing corresponding to the outer peripheral side of the sleeve 31 is used as the first slide bearing 44.
  • a sleeve 37 is provided on the inner circumference of the rotating body (sleeve case 38), and a non-rotating slide bearing corresponding to the inner circumference side of the sleeve 37 is used as a second slide bearing 39.
  • a slide bearing may be held on the outer periphery of the rotating body (rotating shaft 30), and a sleeve may be provided on the corresponding non-rotating body. Further, the first slide bearing holds the sleeve on the outer periphery of the rotating body, and the second slide bearing holds the slide bearing on the outer periphery of the rotating body in a state where the corresponding slide bearing is on the non-rotating side. It is possible that the corresponding sleeve is on the non-rotating side and vice versa.
  • the sleeve case 38 is supplied with water containing slurry or the like in the first clearance 47 and the second clearance.
  • a water supply port 40 for passing water through the clearance 48 is provided.
  • the water that has flowed into the water supply port 40 passes through the first clearance 47 and the second clearance 48 as flow paths.
  • a flow path for allowing water to pass through the first clearance 47 and the second clearance 48 is formed, and the first clearance 47 and the second clearance 48 also function as a flow path. Water quickly flows into the first clearance 47 and the second clearance 48 without staying, and the functions of the first slide bearing 44 and the second slide bearing 39 can be exhibited quickly.
  • first slide bearing 44 and the second slide bearing 39 support the sleeve 31 and the sleeve 37 under dry conditions at the time of start-up, and the sleeve 31 and the sleeve 37 through a very thin liquid film under drainage conditions.
  • the dry condition refers to a condition in which the atmosphere of the first slide bearing 44 and the second slide bearing 39 in operation is in the air without liquid lubrication, and the dry operation is performed under the conditions. That means.
  • the diameter clearance dimension (the first clearance 47)
  • the inner diameter of the first slide bearing 44—the outer diameter of the sleeve 31) and the diameter clearance dimension of the second clearance 48 (the inner diameter of the sleeve 37—the outer diameter of the second slide bearing 39) are the same as those of the first slide bearing 44. It is preferable that the inner diameter is 1/1000 or more and 1/100 or less and the outer diameter of the second slide bearing 39 is 1/1000 or more and 1/100 or less.
  • the first clearance 47 and the second clearance 48 When the dimensions of the first clearance 47 and the second clearance 48 are larger than these ranges, the steady swinging of the rotating shaft 30 becomes large, and the swinging causes the first sliding bearing 44 and the second sliding. The load applied to the bearing 39 is also increased, and stable operation may be difficult. Further, when the dimensions of the first clearance 47 and the second clearance 48 are smaller than these ranges, the first clearance 47 and the second clearance 48 are blocked by foreign matter, or the first slide bearing 44 and the second clearance 48 are closed. In some cases, the second slide bearing 39 may be seized due to friction with foreign matter.
  • the diameter clearance dimension of the first clearance 47 and the diameter clearance dimension of the second clearance 48 are preferably the same, but the first sliding bearing 44, the second sliding bearing 39, the sleeve 37, or the sleeve 31 is made of resin. If these members have elasticity, such as being formed of, the function of the present invention is exhibited even if there is a difference in dimensions.
  • the ratio of the diameter clearance dimension of the second clearance 48 to the diameter clearance dimension of the first clearance 47 is preferably 0.5 or more and 2.0 or less, more preferably 0.7 or more and 1.3. It is as follows.
  • the cushioning is performed.
  • the first slide bearing 44 and the second slide bearing 39 can simultaneously contact the sleeve 31 and the sleeve 37 at the same time, even if the dimensions are not in the above-mentioned range due to the deformation of the material, and the function of the present invention is exhibited.
  • FIG. 4 is a cross-sectional view taken along the line XX ′ shown in FIG. As shown in the figure, the centers of the outer peripheral surface of the sleeve 31, the inner peripheral surface of the first slide bearing 44, the outer peripheral surface of the second slide bearing 39, and the inner peripheral surface of the sleeve 37 substantially coincide with the central axis O. Is configured to do. In FIG. 4, the dimensions of the first clearance 47 and the second clearance 48 are shown enlarged for the sake of convenience.
  • FIG. 5 is a diagram illustrating the operation of the bearing unit during the dry operation.
  • the sleeve 31 fixed to the rotating shaft 30 and the sleeve 37 fixed to the sleeve case 38 also rotate.
  • a bearing reaction force FAN is generated on the rotary shaft 30.
  • a frictional force FAF is generated in a direction opposite to the rotation direction of the rotating shaft 30, and this frictional force FAF causes a whirling vibration in the direction opposite to the rotating direction in the rotating shaft 30. Stabilization power.
  • FIG. 6 is a diagram illustrating the operation of the bearing unit during the drainage operation.
  • the first clearance 47 and the second clearance 48 are filled with water, and this water constitutes a liquid film 49 and a liquid film 50, respectively, whereby the bearing unit functions as a fluid lubrication bearing unit.
  • the liquid film 49 the circumferential direction of the pressure nonuniformity due to the rotation of the rotating shaft 30 occurs, as a result, the radial fluid forces F AR and the circumferential fluid force F AT occurs in the rotation shaft 30.
  • the circumferential fluid force F AT becomes destabilizing force that generates vibrations during drainage operation.
  • the circumferential fluid force F AT is the frictional force F AF generated by the drying operation is a reverse force.
  • the inner surface of the bearing has been formed into a multi-arc shape instead of a perfect circle shape.
  • the inner surface shape of the bearing approaches a perfect circle shape due to wear, and the vibration suppressing effect may be lost.
  • the bearing unit is a sliding bearing that always slides on the sliding surface and supports the rotating shaft in both the normal operation during the dry operation and the drain operation, and the contact of the first sliding bearing, Since the frictional force acting on the contact point of the second sliding bearing cancels out, vibration of the rotating shaft due to the destabilizing force can be suppressed, and stable rotation of the rotating shaft can be maintained.
  • FIG. 7 is a diagram showing the vibration speed when the bearing unit shown in FIG. 3 is provided in the vertical shaft pump and the dry operation without lubrication or cooling with water is performed in the atmosphere in the atmosphere.
  • the 10 has a sleeve 29 on the outer periphery of the rotary shaft 25.
  • the conventional bearing device shown in FIG. A hollow cylindrical slide bearing 28 is provided on the outer peripheral side of the sleeve 29.
  • the outer peripheral surface of the sleeve 29 is configured to face the inner peripheral surface (slip surface) of the slide bearing 28 through a very narrow clearance and slide relative to the slide bearing 28.
  • the diameter and the number of rotations of the rotating shaft 25 and the material of the sleeve 29 and the plain bearing 28 shown in FIG. 10 are the same conditions as the bearing unit shown in FIG.
  • the vertical pump (this embodiment) having the bearing unit shown in FIG. 3 is more constant from the start to the start than the vertical pump having the conventional bearing device. It can be seen that the system is operated at a lower vibration speed than the conventional structure.
  • FIG. 8 is a diagram showing the bearing temperature when the bearing unit shown in FIG. 3 is provided in the vertical shaft pump and the dry operation is performed. For comparison, the bearing temperature when the vertical shaft pump (conventional structure) including the conventional bearing device shown in FIG.
  • the vertical pump (this embodiment) having the bearing unit shown in FIG. 3 is more constant from the start to the stop than the vertical pump having the conventional bearing device. It can be seen that a lower bearing temperature is maintained compared to the conventional structure.
  • FIG. 9 is a diagram showing the vibration speed when the vertical axis pump is provided with the bearing unit shown in FIG. 3 and the drainage operation is performed. During the drainage operation, the bearing unit is submerged in water. For comparison, the vibration speed when the vertical shaft pump (conventional structure) including the conventional bearing device shown in FIG. Note that the results shown in FIG. 9 are obtained by measuring the vibration at the time when the operation condition of the vertical shaft pump is operated under a condition where vibration is likely to occur.
  • the vertical pump (this embodiment) provided with the bearing unit shown in FIG. 3 is more constant from the start to the stop than the vertical pump provided with the conventional bearing device. It can be seen that the system is operated at a lower vibration speed than the conventional structure.
  • the first slide bearing 44 and the second slide bearing 39 are rotated by the rotating body (sleeve) due to the swing of the shaft of the rotary shaft 30 during the dry operation. 31 and the sleeve 37) collide with each other because the frictional forces act in opposite directions to cancel each other at the time of the collision, thereby suppressing the divergence of the swing of the rotating shaft 30 and preventing the vibration due to destabilization. be able to. In addition, it is possible to reduce friction caused by this vibration and suppress an increase in bearing temperature.
  • the bearing unit shown in FIG. 3 has the first slide bearing 44 and the second slide bearing 39, the frictional force of the bearing slide surface during the dry operation is dispersed to suppress heat generation due to the friction of the bearing slide surface. can do.
  • a bearing material having a higher friction coefficient than that of the conventional structure that is, a bearing material having higher wear resistance can be used, and stable operation can be performed for a long period of time.
  • the bearing unit shown in FIG. 3 holds the first slide bearing 44 on the inner peripheral surface of the bearing case 32 and the second slide bearing 39 on the outer peripheral surface thereof. A compact structure can be obtained.
  • the portions (the sleeve 31 and the sleeve 37) located in the water of the rotary shaft 30 are supported by the first slide bearing 44, the second slide bearing 39, and the like.
  • a rolling bearing such as a ball bearing or a roller bearing is not suitable for an underwater bearing of a rotating machine that performs drainage operation, and the effect of this embodiment can be achieved by a sliding bearing.
  • FIG. 11 shows the bearing unit attached to the support member 15 fixed to the inner peripheral surface of the suction bell mouth 1a of the vertical shaft pump in FIG.
  • the rotating shaft 6 has a cylindrical structure with a hollow end.
  • the bearing unit includes a first slide bearing 52 and a second slide bearing 57.
  • a sleeve 51 (corresponding to an example of a sliding portion of the rotating shaft) corresponding to the first slide bearing 52 disposed on the radially outer side of the rotating shaft 6 (around the rotating shaft 6) is a rotating shaft below the impeller.
  • a sleeve 55 (corresponding to an example of a sliding portion of the rotating shaft) corresponding to the second sliding bearing 57 is provided inside the hollow cylindrical structure at the end of the rotating shaft 6 with a cushioning material 56 interposed therebetween.
  • the sleeve 55 and the buffer material 56 corresponding to the second sliding bearing 57 are fixed to the rotating shaft 6 by the pressing plate 58.
  • the first plain bearing 52 is held by a substantially cylindrical first bearing case 54 via a buffer material 53.
  • the first bearing case 54 is fixed to the support member 15.
  • the first bearing case 54 has a substantially disc-shaped collar portion 54a.
  • a flange portion 54a is removably attached to the lower surface of the support member 15 with a bolt 61a so that the first bearing case 54 can be removed vertically downward (suction side) of the pump.
  • the second sliding bearing 57 is disposed immediately below the first sliding bearing 52, and is fixed to the first bearing case 54 by a substantially cylindrical or cylindrical second bearing case 60.
  • the second bearing case 60 has a substantially disc-shaped collar portion 60a, and is detachably attached to the lower surface of the first bearing case 54 of the collar portion 60a by a bolt 61b.
  • the second bearing case 60 is divided from the first bearing case 54,
  • the bearing inspection / maintenance can be improved by removing only the bearing case 60 of the second bearing.
  • the first bearing case 54 When the bearing is replaced, the first bearing case 54 is removed, so that the first slide bearing 52 and the second slide bearing 57 can be removed as a unit at the same time. Can be improved.
  • the diameter of the rotary shaft 6 is relatively small, the size of the device is also relatively small. Therefore, the first bearing case 54 and the second bearing case 60 are not divided parts and are shown in FIG. As described above, it may be an integrated bearing case 62 that holds the first slide bearing 52 and the second slide bearing 57.
  • the integral bearing case 62 has a substantially disc-shaped collar portion 62a, and the collar portion 62a can be fitted to and detached from the lower surface of the support member 15 with a bolt 61c so that the collar portion 62a can be removed vertically below the pump (suction side). Attached to.
  • the second bearing case 60 shown in FIG. 11 and the integrated bearing case 62 shown in FIG. 12 are preferably provided with a plurality of water supply / drain ports (holes) 59.
  • the water supply / drain port 59 By providing the water supply / drain port 59, the water flow of the pump can be reliably guided to the surfaces of the first slide bearing 52 and the second slide bearing 57, and the friction of the bearing surface due to the internal water on the bearing surface can be reduced. The life can be improved and vibration can be suppressed.
  • FIG. 13 is a view showing another embodiment of the bearing unit provided in the vertical shaft pump according to the present invention.
  • the structure of the bearing unit, the outer diameter D 2 of the rotary shaft 6 is applied to the outer diameter D 1 greater than a large vertical shaft pump of the rotary shaft 6 shown in FIG. 11.
  • the second slide bearing 57 is installed on the inner surface of the hollow cylindrical structure of the rotary shaft 6 on the substantially horizontal XX plane at the installation position of the first slide bearing 52.
  • the first slide bearing 52 and the second slide bearing 57 are arranged on the same horizontal plane without being separated in the vertical direction (axial direction), so that the bearing contact at the position facing the same horizontal plane is achieved. Therefore, the bearing sliding stability can be improved without being affected by the bending of the shaft caused by the rotation of the long rotating shaft 6.
  • first slide bearing 52 and the second slide bearing 57 are arranged on the same horizontal plane, it becomes possible to shorten the vertical (axial) length of the bearing unit, and the bearing unit is configured compactly. can do. Since the bearing unit becomes compact, there are fewer parts that obstruct the flow of the handling liquid, and it is possible to reduce adverse effects on pump performance such as a decrease in pump efficiency and an increase in deadline shaft power.
  • FIG. 14 is a view showing a protective cover provided in the vertical shaft pump of the present invention.
  • the protective cover 63 has a substantially spherical shape at the tip, and is attached to the second bearing case 60 by a fixing member 64 so as to be detachable. Further, the protective cover 63 is provided with a water supply / drain port (small hole) 63a for supplying / draining the liquid handled by the pump in the horizontal direction (to face the side).
  • the water supply / drainage port 63a in the protective cover 63 in the horizontal direction (perpendicular to the axial direction of the rotary shaft 6), it is possible to use a drainage pump for rivers or sewers in which slurry is contained in the handling liquid. It is possible to prevent the slurry from entering the bearing portion and suppress the wear of the bearing.
  • the main water supply / drain port 63a drains the water in the bearing portion to the water absorption tank side when the pump is stopped, it is effective in preventing slurry accumulation inside the pump bearing.
  • the protective cover 63 is detachably attached to the second bearing case 60 by the fixing member 64, the protective cover 63 is removed by removing the protective cover 63 during the inspection of the bearing or during the removal / attachment operation. The influence on these operations can be eliminated.
  • the protective cover 63 is detachably attached to the second bearing case 60, but may be detachably attached to the first bearing case 54 or the support member 15.
  • the sleeve 51 is provided on the outer surface of the rotary shaft 6, and the first sliding bearing 52 corresponding to the sleeve 51 is held by the first bearing case 54 outside the sleeve 51.
  • the load of the sliding portion increases.
  • the outer diameter D 3 of the sliding portion of the second plain bearing 57 in the embodiment shown in FIG. 13 is extremely smaller than the outer diameter D 2 of the rotating shaft 6, from the center to the outer periphery of the sleeve 51.
  • the distance from the center to the outer periphery of the second slide bearing 57 are significantly different from each other, so that the second slide bearing 57 cannot receive the surface pressure from the sleeve 55. For this reason, the bearing reaction force of the second sliding bearing 57 is insufficient, and a difference occurs in the frictional forces in the opposite directions applied to the first sliding bearing 52 and the second sliding bearing 57.
  • the bearing unit shown in FIGS. 15 and 16 has a sliding portion that does not directly depend on the diameter of the rotating shaft 6 while ensuring the maintenance such as the ease of replacement and inspection shown in the above description.
  • the present invention provides a bearing unit structure capable of ensuring an optimum peripheral speed, an optimum surface pressure, and an optimum bearing reaction force.
  • FIG. 15 shows a bearing unit according to another embodiment of the present invention attached to a support member 15 fixed to the inner peripheral surface of the suction bell mouth 1a of the vertical shaft pump in FIG.
  • a first bearing case 71 is fixed to the end of the rotating shaft 6 by a fixing member (bolt or the like) 70.
  • the first bearing case 71 has a hollow cylindrical portion 71a, and a sleeve 55 (corresponding to an example of a sliding portion of the rotating shaft) is provided on the inner peripheral surface of the first bearing case 71 via a buffer material 56.
  • the sleeve 55 and the buffer material 56 are fixed to the first bearing case 71 by a pressing plate 58.
  • a first plain bearing 52 is provided on the outer peripheral surface of the cylindrical portion 71 a of the first bearing case 71. Since the first bearing case 71 is fixed to the rotating shaft 6, it rotates together with the rotating shaft 6.
  • a second bearing case 65 is fixed to the support member 15 by a fixing member (bolt or the like) 69.
  • the second bearing case 65 includes a columnar portion 65 a inserted into a hollow portion (inside the cylinder) of the hollow cylindrical portion 71 a of the first bearing case 71, and a hollow cylindrical shape of the first bearing case 71. And a cylindrical portion 65b surrounding the outer periphery of the portion 71a.
  • a second sliding bearing 57 is provided on the outer peripheral surface of the columnar portion 65a corresponding to the sleeve 55 provided on the inner peripheral surface of the hollow cylindrical portion 71a of the first bearing case 71 via a buffer material 56. Is provided.
  • a sleeve 51 (through a buffer material 53 is provided corresponding to the first sliding bearing 52 provided in the first bearing case 71. Corresponding to an example of the sliding portion of the rotating shaft).
  • the sleeve 51 and the buffer material 53 are fixed to the second bearing case 65 by a pressing plate 66.
  • the outer diameter D 2 ′ of the sliding portion of the first sliding bearing 52 is smaller than the outer diameter D 2 of the rotating shaft 6, and when the rotating shaft 6 rotates, the peripheral speed of the sliding portion is that of the sliding member. It is set so that proper use can be continued. Further, the outer diameter D 3 of the sliding portion of the second sliding bearing 57 is smaller than the outer diameter D 2 ′ of the sliding portion of the first sliding bearing 52, but the second sliding bearing 57 is removed from the sleeve 55. It is the size of the range where the surface pressure can be properly received.
  • the size of the first bearing case 71 and the second bearing case 65 can be made compact without depending much on the diameter of the rotating shaft 6.
  • the first sliding bearing 52 and the second sliding bearing 57 can be inspected and replaced by removing only the second bearing case 65, so that workability is improved.
  • the first bearing case 71 having sliding portions on the inner peripheral surface and the outer peripheral surface is fixed to the end of the rotating shaft 6, and the inner peripheral surface and the outer peripheral surface of the first bearing case 71 are fixed.
  • a second bearing case 65 having a sliding portion corresponding to the sliding portion is fixed to a non-rotating fixed body such as the support member 15.
  • FIG. 16 shows a bearing unit structure according to another embodiment of the present invention attached to a support member 15 fixed to the inner peripheral surface of the suction bell mouth 1a of the vertical shaft pump in FIG.
  • a first bearing case 72 is fixed to the end of the rotating shaft 6 by a fixing member (bolt or the like) 77.
  • the first bearing case 72 has a columnar portion 72a and a hollow cylindrical portion 72b surrounding the columnar portion 72a.
  • a second slide bearing 57 (corresponding to an example of a sliding portion of the rotating shaft) is provided on the outer periphery of the columnar portion 72a, and a sleeve 51 (rotation) is provided on the inner surface of the cylindrical portion 72b via a buffer material 53.
  • the sleeve 51 and the buffer material 53 are fixed to the first bearing case 72 by a pressing plate 79. Since the first bearing case 72 is fixed to the rotating shaft 6, it rotates together with the rotating shaft 6.
  • a second bearing case 73 is fixed to the support member 15 by a fixing member (bolt or the like) 74.
  • the second bearing case 73 has a cylindrical portion 73a inserted between the columnar portion 72a and the cylindrical portion 72b of the first bearing case 72.
  • a sleeve 55 corresponding to the second sliding bearing 57 is provided on the inner peripheral surface of the cylindrical portion 73 a of the second bearing case 73 via a cushioning material 56.
  • the sleeve 55 and the buffer material 56 are fixed to the second bearing case 73 by a pressing plate 80.
  • a first plain bearing 52 corresponding to the sleeve 51 is provided on the outer peripheral surface of the cylindrical portion 73 a of the second bearing case 73.
  • the outer diameter D 2 ′ of the sliding portion of the first sliding bearing 52 is smaller than the outer diameter D 2 of the rotating shaft 6, and when the rotating shaft 6 rotates, the peripheral speed of the sliding portion is that of the sliding member. It is set so that proper use can be continued. Further, the outer diameter D 3 of the sliding portion of the second sliding bearing 57 is smaller than the outer diameter D 2 ′ of the sliding portion of the first sliding bearing 52, but the second sliding bearing 57 has the sleeve 55. It is the size of the range where the surface pressure can be properly received.
  • first slide bearing 52 and the second slide bearing 57 of this bearing unit As materials for the first slide bearing 52 and the second slide bearing 57 of this bearing unit, ceramics, resin, rubber, or the like can be used. In the standby standby pump that performs air operation and drainage operation, it can be used in an anhydrous state rather than a brittle material such as ceramics in order to prevent damage to the bearing due to a sudden change in operating state (including a sudden change in bearing temperature). A resin or a resin composite material is used. When such a resin bearing is used, since the resin bearing is inferior in wear resistance and has a large friction coefficient compared to a ceramic bearing, there arises a problem that the amount of heat generated by the bearing during air operation increases. However, by using the combination unit of the first slide bearing 52 and the second slide bearing 57 of the present invention, it is possible to suppress the amount of wear and heat generation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne une pompe à arbre vertical qui, même pour des pompes de grande capacité, permet un remplacement aisé des paliers immergés lorsque la pompe est installée sans soulever la pompe, et possède une fiabilité accrue des paliers immergés. La pompe à arbre vertical selon l'invention est pourvue d'un carter de guidage (1), d'un tube suspendu (3) qui suspend le carter de guidage (1) à l'intérieur d'un réservoir d'eau (5), d'un tube courbé de décharge (4) qui est relié à l'extrémité supérieure du tube suspendu (3), d'une roue à aubes (10) qui est logée à l'intérieur du carter de guidage (1), et d'un arbre rotatif (6) qui est fixé à la roue à aubes (10). L'arbre rotatif (6) est supporté en rotation par une unité à palier immergé (12) et un palier externe (11). L'unité à palier immergé (12) est positionnée au-dessous de la roue à aubes (10) et supporte l'extrémité inférieure de l'arbre rotatif (6). L'arbre rotatif (6) s'étend du palier extérieur (11) à la roue à aubes (10) sans passer à travers des paliers autres que le palier extérieur (11). L'unité à palier immergé (12) possède un palier de contact interne qui supporte une partie coulissante de l'arbre rotatif (6) sur une surface circonférentielle intérieure de palier, et possède un palier de contact externe qui supporte la partie coulissante de l'arbre rotatif (6) sur une surface circonférentielle externe de palier.
PCT/JP2015/069985 2014-07-14 2015-07-13 Pompe à arbre vertical WO2016009977A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
SG11201610976PA SG11201610976PA (en) 2014-07-14 2015-07-13 Vertical pump
CN201580038340.6A CN106662109B (zh) 2014-07-14 2015-07-13 立轴泵

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014-144050 2014-07-14
JP2014144050A JP6320208B2 (ja) 2014-07-14 2014-07-14 立軸ポンプ

Publications (1)

Publication Number Publication Date
WO2016009977A1 true WO2016009977A1 (fr) 2016-01-21

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PCT/JP2015/069985 WO2016009977A1 (fr) 2014-07-14 2015-07-13 Pompe à arbre vertical

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JP (1) JP6320208B2 (fr)
CN (1) CN106662109B (fr)
MY (1) MY176184A (fr)
SG (1) SG11201610976PA (fr)
WO (1) WO2016009977A1 (fr)

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Publication number Priority date Publication date Assignee Title
CN106574623B (zh) * 2014-08-22 2018-12-11 株式会社荏原制作所 立轴泵
JP7345990B2 (ja) * 2020-02-17 2023-09-19 株式会社電業社機械製作所 立軸ポンプ

Citations (3)

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JP2001289191A (ja) * 2001-02-26 2001-10-19 Hitachi Ltd ポンプの軸受装置
JP2009074530A (ja) * 2007-08-30 2009-04-09 Torishima Pump Mfg Co Ltd ポンプの軸受診断装置及びその方法
JP2010285885A (ja) * 2009-06-09 2010-12-24 Torishima Pump Mfg Co Ltd 水中軸受

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JPS6023676A (ja) * 1983-07-15 1985-02-06 Fujitsu Ltd 潤滑ガスのラビリンス構造
JPH0694035A (ja) * 1992-09-10 1994-04-05 Hitachi Ltd 立軸排水ポンプ用軸受装置
JP2000002190A (ja) * 1998-06-15 2000-01-07 Kubota Corp 立軸ポンプのすべり軸受装置
JP3930734B2 (ja) * 2001-12-28 2007-06-13 株式会社荏原製作所 立軸ポンプ
JP2007016884A (ja) * 2005-07-07 2007-01-25 Ge Medical Systems Global Technology Co Llc 軸受機構およびｘ線管
JP2009204034A (ja) * 2008-02-27 2009-09-10 Ishigaki Co Ltd 滑り軸受ユニット及びこの滑り軸受ユニットを用いた先行待機型ポンプ
CN202707510U (zh) * 2012-06-20 2013-01-30 天津长芦海晶集团有限公司 一种盐田用卤水泵

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Publication number Priority date Publication date Assignee Title
JP2001289191A (ja) * 2001-02-26 2001-10-19 Hitachi Ltd ポンプの軸受装置
JP2009074530A (ja) * 2007-08-30 2009-04-09 Torishima Pump Mfg Co Ltd ポンプの軸受診断装置及びその方法
JP2010285885A (ja) * 2009-06-09 2010-12-24 Torishima Pump Mfg Co Ltd 水中軸受

Also Published As

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SG11201610976PA (en) 2017-02-27
MY176184A (en) 2020-07-24
JP6320208B2 (ja) 2018-05-09
CN106662109A (zh) 2017-05-10
JP2016020648A (ja) 2016-02-04
CN106662109B (zh) 2018-12-14

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