WO2015098896A1 - Dispositif de palier et pompe - Google Patents

Dispositif de palier et pompe Download PDF

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Publication number
WO2015098896A1
WO2015098896A1 PCT/JP2014/084007 JP2014084007W WO2015098896A1 WO 2015098896 A1 WO2015098896 A1 WO 2015098896A1 JP 2014084007 W JP2014084007 W JP 2014084007W WO 2015098896 A1 WO2015098896 A1 WO 2015098896A1
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WO
WIPO (PCT)
Prior art keywords
lubricating oil
oil
bearing
disk
rotating shaft
Prior art date
Application number
PCT/JP2014/084007
Other languages
English (en)
Japanese (ja)
Inventor
成 吉川
栄作 兼村
平田　和也
山中　隆司
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 JP2015554908A priority Critical patent/JPWO2015098896A1/ja
Publication of WO2015098896A1 publication Critical patent/WO2015098896A1/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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/049—Roller 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/0462—Bearing cartridges
    • 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
    • F04D29/06—Lubrication
    • F04D29/061—Lubrication especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/6666—Details of supply of the liquid to the bearing, e.g. passages or nozzles from an oil bath in the bearing housing, e.g. by an oil ring or centrifugal disc
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6685—Details of collecting or draining, e.g. returning the liquid to a sump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated
    • F16N7/14—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated the lubricant being conveyed from the reservoir by mechanical means
    • F16N7/16—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated the lubricant being conveyed from the reservoir by mechanical means the oil being carried up by a lifting device
    • F16N7/18—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated the lubricant being conveyed from the reservoir by mechanical means the oil being carried up by a lifting device with one or more feed members fixed on a shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement

Definitions

  • the present invention relates to a bearing device used for a horizontal shaft pump or the like, and more particularly, to a bearing device capable of appropriately supplying lubricating oil to a bearing even when the diameter of a rotating shaft is increased or the rotational speed is increased. .
  • the present invention also relates to a pump provided with such a bearing device.
  • a bearing device is disposed in the vicinity of the end of the rotary shaft in order to rotatably support the rotary shaft.
  • a lubricating oil storage tank in which lubricating oil for lubricating and cooling the bearing is stored is provided inside or outside the bearing device. Examples of means for supplying lubricating oil from the lubricating oil storage tank to the bearing include a forced oil supply device using external power or a self-lubricating device that does not use external power.
  • the forced oil supply device supplies lubricating oil to a bearing arranged inside the bearing device using external power from a lubricating oil storage tank arranged outside the bearing device.
  • the lubricating oil is pumped up from the lubricating oil storage tank disposed below the rotating shaft inside the bearing device by using the rotational force of the rotating shaft and supplied to the bearing.
  • FIG. 11 is a cross-sectional view showing a bearing device when a forced oil supply device is used.
  • FIG. 12 is a piping and instrument system diagram of the forced oiling device.
  • FIG. 13A and FIG. 13B are a schematic side view and a schematic plan view showing the arrangement of the pump when the forced oil supply device is used.
  • the rotary shaft 1 of the horizontal shaft pump 100 extends horizontally, and the end of the rotary shaft 1 is rotatably supported by bearings 9A and 9B.
  • a forced oil supply device 26 is disposed outside the horizontal shaft pump 100. Lubricating oil is forcibly supplied from the forced oil supply device 26 to the bearings 9A and 9B.
  • the forced oil supply device 26 includes a plurality of components such as a lubricating oil pump 21, a filter 24, a lubricating oil cooler 23, a plurality of hydraulic pressure monitoring instruments 25, and a lubricating oil tank 22. Therefore, the cost of the forced oil supply device 26 is increased.
  • the installation space of the forced oil supply device 26 is required.
  • the installation space for the forced oil supply apparatus 26 since the volume of each component which comprises the forced oil supply apparatus 26 is large, the installation space for the forced oil supply apparatus 26 also becomes large. As a result, the installation space required for the entire pump system becomes large, which may cause a reduction in product competitiveness in the market as a rotating machine.
  • FIG. 14 shows an example of a conventional bearing device using a self-lubricating device.
  • the edge part of the rotating shaft 1 is rotatably supported by bearing 9A, 9B.
  • the lubricating oil storage tank 10 in which the lubricating oil is stored is disposed below the bearings 9A and 9B.
  • An oil ring 20 is provided as a self-lubricating device for scooping up the lubricating oil in the lubricating oil storage tank 10.
  • the oil ring 20 is disposed so as to surround the outer peripheral surface of the rotating shaft 1 and rotates with the rotation of the rotating shaft 1.
  • the lubricating oil is supplied to the bearings 9 ⁇ / b> A and 9 ⁇ / b> B by scooping up the lubricating oil in the lubricating oil storage tank 10 by the rotating oil ring 20.
  • Such a self-lubricating device using the oil ring 20 is conventionally known as an oil ring self-lubricating device.
  • the circumferential speed (hereinafter simply referred to as the circumferential speed) of the outer peripheral surface of the rotating shaft 1 due to the increase in the diameter of the rotating shaft 1 or the speeding up of the rotating shaft 1 or the like. )
  • the rotation of the oil ring 20 cannot follow the rotation of the rotary shaft 1. That is, the rotational speed of the oil ring 20 with respect to the rotating shaft 1 is greatly reduced, and the oil ring 20 cannot properly scoop up the lubricating oil. As a result, desired lubrication performance and cooling performance cannot be obtained.
  • the lubricating oil overflows and scatters from the outer circumferential arc surface, or the lubricating oil scatters from a portion other than the outer circumferential arc surface.
  • the lubricating oil is lifted above the outer periphery of the disk through the flexible tube using the pressure of the lubricating oil gathered at the outer edge of the disk by centrifugal force, and further provided outside the flexible tube. Supplied to the journal bearing through the introduced hole. For this reason, the entire bearing device is large in the radial direction, and the processing of the introduction hole is complicated and takes time.
  • Patent Document 3 discloses a technique for guiding oil pumped up by an oil ring to a bearing.
  • the amount of lubricating oil supplied to the bearing when this technology is used varies depending on operating conditions. Further, the above-described problem that the oil ring does not follow the rotation shaft as the rotation shaft rotates at high speed is not taken into consideration. Further, it is predicted that the amount of lubricating oil flying from the oil surface due to the rotation of the oil ring increases as the peripheral speed of the rotating shaft increases.
  • no consideration is given to the loss of lubricating oil in the axial direction of the rotating shaft, and there is a concern about oil leakage from the shaft seal portion or the like of the bearing device.
  • the above-described conventional self-lubricating bearing device provides an appropriate self-lubricating technique considering the rotational speed, the diameter of the rotating shaft, the viscosity of the lubricating oil to be used, and the oil viscosity change due to the ambient temperature and operating time. It's hard to say. Further, in other related literatures and prior arts, there is no technique related to suppressing an excessive amount of lubricating oil supplied and optimizing the amount of lubricating oil supplied.
  • the present invention has been made in view of the above-described conventional problems, and even when the peripheral speed of the rotating shaft is increased, the lubricating oil can be stably supplied to the bearing in an appropriate amount. And it aims at providing the bearing apparatus which is compact compared with the past, and does not require a complicated process. Moreover, an object of this invention is to provide the pump provided with such a bearing apparatus.
  • One aspect of the present invention for solving the above-described problems is a bearing that receives a load of a rotating shaft, a lubricating oil storage tank that is disposed below the bearing, and is fixed to the rotating shaft so as to be integrated with the rotating shaft.
  • An oil disk that pumps up the lubricating oil stored in the lubricating oil storage tank by rotating, a lubricating oil passage that extends to the bearing, and a guide casing that guides the lubricating oil pumped up by the oil disk to the lubricating oil passage
  • the guide casing has an inner surface facing a side surface and an outer peripheral surface of the oil disk.
  • a lubricating oil introduction groove connected to the lubricating oil passage is formed on an inner surface of the guide casing, and the lubricating oil introduction groove is adjacent to a side surface of the oil disk. It is characterized by that.
  • the lubricating oil passage extends from the inner surface of the guide casing in the axial direction of the rotating shaft, and further extends in a direction perpendicular to the axial direction to reach the bearing. .
  • an annular groove is provided on the outer peripheral surface of the oil disk.
  • a plurality of depressions are provided on the outer peripheral surface of the oil disk.
  • a plurality of radial grooves are provided on a side surface of the oil disk.
  • a key is provided on the outer peripheral surface of the rotating shaft, and a key groove is formed on an inner peripheral surface of a through hole formed at the center of the oil disk.
  • the oil disk is fixed to the rotating shaft in a state in which the groove is engaged.
  • the bearing is one of at least two bearings arranged in series on the rotating shaft, and an annular spacer is arranged between the at least two bearings. It is characterized by that.
  • the spacer has an oil supply hole extending from an outer peripheral surface to an inner peripheral surface, and the oil supply hole is connected to the lubricating oil passage.
  • the bearing is a thrust bearing that receives an axial load of the rotating shaft.
  • the thrust bearing is configured to receive both an axial load and a radial load of the rotating shaft.
  • Another aspect of the present invention is a pump including a rotating shaft, an impeller fixed to the rotating shaft, and the bearing device that rotatably supports the rotating shaft.
  • the oil disk always rotates at the same rotational speed as the rotational shaft, even if the rotational speed of the rotational shaft increases, slippage does not occur and the follow-up performance does not decrease as in the conventional oil ring. . Therefore, according to the present invention, it is possible to stably supply the lubricating oil to the bearing even under the high peripheral speed condition of the rotating shaft, which is difficult to supply with conventional technology such as an oil ring. As a result, the forced oiling device is not required, the installation area of the pump is reduced, and the cost is reduced, so that the product competitiveness in the market can be increased.
  • the oil disk is surrounded by a guide casing disposed opposite to and in close proximity to the oil disk, it is possible to prevent wasteful splashing of the lubricating oil scooped up by the oil disk. As a result, an amount of lubricating oil more than necessary and sufficient can be led to the lubricating oil passage leading to the bearing. Since the lubricating oil passage extends in the axial direction at a position close to the rotating shaft, a compact bearing device can be provided as compared with the conventional one without requiring complicated processing.
  • the amount of lubricating oil supplied to the bearing is determined by the circumferential position of the lubricating oil passage port and the shape of the passage (cross-sectional area, length, passage direction with respect to the oil disk rotation direction, flow resistance factors such as surface roughness, Alternatively, the amount is limited to a suitable amount by an excessive lubricating oil discharge hole provided in the course of the passage. Therefore, an increase in rotation loss due to the excessive supply of lubricating oil and the accompanying heat generation are prevented.
  • FIG. 1 is a cross-sectional view showing an example of a horizontal shaft single-stage pump provided with a bearing device according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view showing an example of a horizontal shaft multi-stage pump provided with a bearing device according to an embodiment of the present invention.
  • FIG. 3 is a cross-sectional view showing the structure of a self-lubricating bearing device according to an embodiment of the present invention.
  • FIG. 4A is a longitudinal sectional view of the oil disk.
  • FIG. 4B is a partial plan view of the oil disk shown in FIG. 4A as viewed from the axial direction.
  • FIG. 4C is a perspective view of the oil disc shown in FIG. 4A.
  • FIG. 5A is a longitudinal sectional view of another example oil disk.
  • FIG. 5B is a partial plan view of the oil disk shown in FIG. 5A as viewed from the axial direction.
  • FIG. 5C is a perspective view of the oil disk shown in FIG. 5A.
  • FIG. 6A is a longitudinal sectional view of still another example of an oil disk.
  • FIG. 6B is a partial plan view of the oil disk shown in FIG. 6A as viewed from the axial direction.
  • 6C is a perspective view of the oil disk shown in FIG. 6A.
  • FIG. 7 is an enlarged sectional view showing the oil disk and the guide casing.
  • FIG. 8 is a view showing an inner side surface of a guide casing provided with a plurality of lubricating oil introduction grooves.
  • FIG. 9 is a view showing the inner surface of the guide disk that is not provided with the lubricating oil introduction groove and that faces the side surface of the oil disk.
  • FIG. 10A is a cross-sectional view showing a part of the bearing device along the longitudinal direction of the rotating shaft.
  • FIG. 10B is a diagram showing a cross section of the bearing device as viewed from the longitudinal direction of the rotating shaft.
  • FIG. 11 is a cross-sectional view showing a bearing device when a forced oil supply device is used.
  • FIG. 12 is a piping and instrument system diagram of the forced oiling device.
  • FIG. 13A is a schematic side view showing the arrangement of pumps when a forced oiling device is used.
  • FIG. 13B is a schematic plan view showing the arrangement of the pumps when the forced oiling device is used.
  • FIG. 14 is a cross-sectional view showing an example of a conventional bearing device using a self-lubricating device.
  • FIG. 1 is a cross-sectional view showing an example of a horizontal shaft single-stage pump provided with a bearing device according to an embodiment of the present invention.
  • a horizontal axis single-stage pump 100 as a rotating machine shown in FIG. 1 has an impeller 2 and a rotating shaft 1 to which the impeller 2 is fixed.
  • the rotating shaft 1 extends horizontally.
  • One end of the rotary shaft 1 is connected to a drive machine such as an electric motor (not shown), and the rotary shaft 1 and the impeller 2 are rotated by this drive machine.
  • the rotating shaft 1 is rotatably supported by bearing devices 9 and 9 provided in the vicinity of both ends thereof.
  • the impeller 2 is disposed in the pump casing 5.
  • the pump casing 5 shown in FIG. 1 has a spiral chamber 5a therein, and the impeller 2 is disposed in the spiral chamber 5a.
  • a liquid such as water is sucked from the suction port 3
  • the pressure of the liquid is increased by the action of the impeller 2 and the spiral chamber 5 a, and the liquid is discharged from the discharge port 4. It is.
  • the impeller 2 in the illustrated example has a double suction structure for sucking liquid from both sides.
  • the caps 2A and 2B are attached to the liquid inlet of the impeller 2, respectively.
  • a thrust force due to a pressure difference can be applied in one direction of the rotating shaft 1 and the rotating shaft 1 can be rotated in a stable state.
  • This thrust force is supported by a thrust bearing unit 9A of the bearing device 9. Since a thrust force acts on the thrust bearing unit 9A as a load, it is necessary to supply an appropriate amount of lubricating oil to the thrust bearing unit 9A and cool the thrust bearing unit 9A while lubricating it.
  • two radial bearing units 9B and 9B are disposed in the vicinity of both end portions of the rotary shaft 1.
  • the rotary shaft 1 is supported by a total of three bearings including these two radial bearing units 9B and 9B and one thrust bearing unit 9A.
  • sleeve-type bearings are used for the radial bearing units 9B and 9B, and a conventional self-lubricating oil supply device having an oil ring 20 is provided in the sleeve-type radial bearing units 9B and 9B. It has been adopted.
  • the configuration of the present invention described later is applied to the thrust bearing unit 9A.
  • FIG. 2 is a cross-sectional view showing an example of a horizontal multistage pump provided with a bearing device according to an embodiment of the present invention.
  • a horizontal axis multistage pump 100 as a rotating machine shown in FIG. 2 includes a plurality of impellers 2 and a rotary shaft 1 to which the impellers 2 are fixed.
  • the rotating shaft 1 extends horizontally.
  • the plurality of impellers 2 are arranged in series on the rotary shaft 1, and a plurality of guide vanes 6 are arranged so as to surround each of the impellers 2.
  • One end of the rotary shaft 1 is connected to a drive machine such as an electric motor (not shown), and the rotary shaft 1 and the impeller 2 are rotated by this drive machine.
  • the rotating shaft 1 is rotatably supported by bearing devices 9 and 9 provided in the vicinity of both ends thereof.
  • the impeller 2 is disposed in the pump casing 5.
  • liquid such as water is sucked from the suction port 3, and the pressure of the liquid is increased by the action of the impeller 2 and the guide vane 6, and the liquid is discharged from the discharge port. 4 is spit out.
  • the plurality of impellers 2 are arranged in the same direction, the thrust force generated by the pressure difference between the adjacent impellers 2 is overlapped by the number of impellers 2, and a large thrust force is generated.
  • This thrust force is offset by the balance device 7 provided in the horizontal multistage pump 100, but a certain amount of thrust force remains during transient operation.
  • This residual thrust force is supported by the thrust bearing unit 9A of the bearing device 9. Since the residual thrust force acts on the thrust bearing unit 9A as a load, it is necessary to supply an appropriate amount of lubricating oil to the thrust bearing unit 9A and cool the thrust bearing unit 9A while lubricating it.
  • two radial bearing units 9B and 9B are disposed in the vicinity of both end portions of the rotary shaft 1.
  • the rotary shaft 1 is supported by a total of three bearings including these two radial bearing units 9B and 9B and one thrust bearing unit 9A.
  • sleeve-type bearings are used for the radial bearing units 9B and 9B, and a conventional self-lubricating oil supply device having an oil ring 20 is provided in the sleeve-type radial bearing units 9B and 9B. It has been adopted.
  • the configuration of the present invention described later is applied to the thrust bearing unit 9A.
  • the configuration of the bearing devices 9 and 9 disposed in the vicinity of both ends of the rotary shaft 1 is the same as that of the horizontal axis single-stage pump shown in FIG.
  • the rotary shaft 1 extends through the pump casing 5 in both cases of the horizontal shaft pump 100 shown in FIGS.
  • a gap between the rotary shaft 1 and the pump casing 5 is sealed by shaft sealing devices 8 and 8 such as mechanical seals. Therefore, the liquid pressurized by the impeller 2 does not enter the bearing devices 9 and 9.
  • FIG. 3 is a cross-sectional view showing the structure of a self-lubricating bearing device according to an embodiment of the present invention.
  • the bearing device 9 includes a thrust bearing unit 9 ⁇ / b> A that receives the axial load and the radial load of the rotating shaft 1 that extends horizontally, and a radial bearing unit 9 ⁇ / b> B that receives the radial load of the rotating shaft 1.
  • a thrust bearing unit 9 ⁇ / b> A that receives the axial load and the radial load of the rotating shaft 1 that extends horizontally
  • a radial bearing unit 9 ⁇ / b> B that receives the radial load of the rotating shaft 1.
  • a plurality of angular ball bearings are used for the thrust bearing unit 9A.
  • a lubricating oil storage tank 10 is disposed below the thrust bearing unit 9A and the radial bearing unit 9B, and the oil level of the lubricating oil stored in the lubricating oil storage tank 10 is indicated by a dotted line with a reference numeral 10A. ing.
  • the amount of lubricating oil is controlled so that the oil level 10A in the lubricating oil storage tank 10 is constant.
  • a cooling jacket 27 is provided below the lubricating oil storage tank 10, and the lubricating oil in the lubricating oil storage tank 10 is cooled by the coolant flowing through the cooling jacket 27.
  • an air cooling structure with fins may be employed. Or it is good also as a structure which inserts a cooling liquid tube with a fin in the lubricating oil storage tank 10, and cools lubricating oil directly.
  • the bearing device 9 further includes a lubricating oil pumping means 11 that is fixed to the rotating shaft 1 and rotates together with the rotating shaft 1 to pump up the lubricating oil stored in the lubricating oil storage tank 10.
  • the lubricating oil lifting means 11 is configured as a circular oil disk.
  • the oil disk 11 is fixed to the rotary shaft 1 so as to rotate integrally with the rotary shaft 1.
  • a key 1 a is provided on the outer peripheral surface of the rotating shaft 1
  • a key groove 11 a is formed on the inner peripheral surface of a through hole formed at the center of the oil disk 11.
  • the rotary shaft 1 is inserted into the through hole of the oil disk 11 so that the key 1a is inserted into the key groove 11a.
  • the torque of the rotary shaft 1 is transmitted to the oil disc 11, and the oil disc 11 rotates integrally with the rotary shaft 1. Therefore, the oil disk 11 always rotates at the same rotational speed as the rotary shaft 1.
  • the lower part of the oil disk 11 is immersed in the lubricating oil in the lubricating oil storage tank 10, and the rotating oil disk 11 scoops up the lubricating oil stored in the lubricating oil storage tank 10.
  • various undulating shapes may be provided on the peripheral edge of the oil disk 11.
  • FIGS. 4A to 4C are diagrams showing an example in which an annular groove 12 is provided on the outer peripheral surface of the oil disk 11.
  • FIG. As shown in FIGS. 4A to 4C, an annular groove 12 extending in the circumferential direction is provided on the outer peripheral surface of the oil disk 11. A part of the outer peripheral surface of the oil disk 11 is always immersed in the lubricating oil in the lubricating oil storage tank 10. When the oil disk 11 rotates, the lubricating oil is held in the annular groove 12 formed on the outer peripheral surface thereof, so that it is possible to increase the amount of lubricating oil that the oil disk 11 scoops up.
  • FIGS. 5A to 5C are views showing an example in which a plurality of depressions 13 are provided on the outer peripheral surface of the oil disk 11. As shown in FIGS. 5A to 5C, a plurality of depressions 13 are provided on the outer peripheral surface of the oil disk 11. These recesses 13 are arranged at equal intervals along the circumferential direction of the oil disk 11. When the oil disk 11 rotates, the lubricating oil is held in the plurality of recesses 13 formed on the outer peripheral surface thereof, so that the amount of lubricating oil that the oil disk 11 scoops up can be increased.
  • the recess 13 of the present embodiment is conical, but may have other shapes such as a cylindrical shape.
  • FIGS. 6A to 6C are views showing an example in which a plurality of radial grooves 14 are provided on both side surfaces of the oil disk 11.
  • a plurality of radial grooves 14 extending in the radial direction of the oil disk 11 are provided on both side surfaces of the oil disk 11.
  • the plurality of radial grooves 14 are arranged at equal intervals around the center of the oil disk 11. These radial grooves 14 extend to the outer peripheral surface of the oil disk 11, and the outer end of each radial groove 14 is on the outer peripheral surface of the oil disk 11.
  • the lubricating oil is held in the radial grooves 14 formed on both side surfaces thereof, so that the amount of lubricating oil that the oil disk 11 scoops up can be increased.
  • the radial groove 14 of the illustrated embodiment extends in the radial direction of the oil disk 11, the radial groove 14 may be inclined from the radial direction. The radial groove in this case also extends to the outer peripheral surface of the oil disk 11. The radial groove may be inclined toward the rotation direction of the oil disk 11 or may be inclined toward a direction opposite to the rotation direction. The amount of lubricating oil that the oil disk 11 scoops up can be adjusted by the inclination direction and the inclination angle of the radial groove.
  • FIG. 7 is an enlarged cross-sectional view showing the oil disk 11 and the guide casing 15. As shown in FIG. 7, the guide casing 15 is disposed in the vicinity of the oil disk 11.
  • the guide casing 15 is composed of two annular guide disks 15A and 15B arranged to face both side surfaces (two side surfaces aligned in the axial direction) of the oil disk 11. In the example illustrated in FIG.
  • the guide casing 15 includes two guide disks 15 ⁇ / b> A and 15 ⁇ / b> B that are arranged so as to sandwich both side surfaces of the oil disk 11. Further, the guide casing 15 is disposed in the vicinity of the outer peripheral surface of the oil disk 11. The outer peripheral surface of the oil disk 11 is the outermost peripheral surface located between both side surfaces of the oil disk 11.
  • the inner surface of the guide casing 15 is disposed close to both side surfaces and the outer peripheral surface of the oil disk 11 and faces both side surfaces and the outer peripheral surface of the oil disk 11. More specifically, in the example shown in FIG. 7, annular guide disks 15 ⁇ / b> A and 15 ⁇ / b> B are arranged so as to face both side surfaces of the oil disk 11, and the outer peripheral surface of the oil disk 11 is also surrounded by the guide casing 15. ing. Between the oil disk 11 and the guide casing 15, an axial gap W1 and a radial gap W2 are formed.
  • the axial gap W ⁇ b> 1 is a gap between the side surface of the oil disk 11 and the guide casing
  • the radial gap W ⁇ b> 2 is a gap between the outer peripheral surface of the oil disk 11 and the guide casing 15.
  • gaps W1 and W2 are set to appropriate values so that the lubricating oil pumped up on the oil disk 11 does not scatter or fall based on the pump operating conditions such as the viscosity of the lubricating oil used and the rotational speed of the rotary shaft 1.
  • the axial gap W1 is 2 mm to 4 mm
  • the radial gap W2 is 3 mm to 6 mm.
  • the guide casing 15 surrounding the oil disk 11 is disposed close to the oil disk 11 at a suitable distance.
  • the lubricating oil pumped up on the oil disk 11 is scattered from the oil disk 11, the lubricating oil accompanies the rotation direction due to the rotation of the oil disk 11, and the oil disk 11 and the guide casing 15
  • the gaps W1 and W2 are held. Accordingly, the amount of lubricating oil held in the gaps W1 and W2 is appropriately adjusted according to the dimensions of the gaps W1 and W2 between the oil disk 11 and the guide casing 15.
  • the lubricating oil pumped up by the oil disk 11 is directly guided to the lubricating oil passage 17 (described later) and the communication passage 28 extending in the axial direction and directly communicating with the bearing 32 constituting the thrust bearing unit 9A.
  • the supply amount of the lubricating oil can be adjusted. Therefore, the amount of lubricating oil supplied to the thrust bearing unit 9A is appropriately maintained. Furthermore, since the splashing range of the lubricating oil scooped up from the oil disk 11 by the guide casing 15 is limited, leakage of the lubricating oil from the shaft seal device 8 can be prevented.
  • the axial gap W1 and the radial gap W2 are appropriately set according to the pump type and / or pump operating conditions (for example, the viscosity of the lubricating oil and the rotational speed of the rotary shaft 1).
  • a plurality of lubricating oil introduction grooves 16 are provided on the inner surface (inner side surface) of the guide casing 15 that faces the side surface of the oil disk 11. More specifically, as shown in FIG. 7, a plurality of lubricating oil introduction grooves 16 are provided on the inner surface of the guide disk 15A disposed closer to the thrust bearing unit 9A than the guide disk 15B. These lubricating oil introduction grooves 16 are disposed close to the side surface of the oil disk 11 and extend from the vicinity of the rotating shaft 1 in the radially outward direction of the oil disk 11. The outer end of the lubricating oil introduction groove 16 is connected to an inlet 17a of a lubricating oil passage 17 that sends the lubricating oil to the thrust bearing unit 9A.
  • FIG. 8 is a view showing an inner side surface of the guide casing 15 provided with a plurality of lubricating oil introduction grooves 16.
  • three lubricating oil introduction grooves 16 are provided, and these lubricating oil introduction grooves 16 are located in the upper half of the guide casing 15.
  • the lubricating oil introduction groove 16 is connected to a lubricating oil passage 17 for supplying the lubricating oil pumped up by the oil disk 11 to the thrust bearing unit 9A.
  • the guide casing 15 surrounds the oil disk 11 with the limited gaps W1 and W2 so that the lubricating oil pumped up by the oil disk 11 is not scattered unnecessarily.
  • the lubricating oil accompanying the rotation direction in the gaps W1 and W2 between the oil disks 11 flows along the lubricating oil introduction groove 16, and is guided to the inlet 17a of the lubricating oil passage 17.
  • the lubricant introduction groove 16 is provided to guide the lubricant from the gaps W1 and W2 between the guide casing 15 and the oil disk 11 to the lubricant passage 17. Therefore, the lubricating oil passage 17 is formed in the bearing casing 35 that accommodates the thrust bearing unit 9A and the radial bearing unit 9B.
  • the cooling jacket 27 described above is also formed in the bearing casing 35.
  • the direction in which the lubricating oil introduction groove 16 extends from the inlet 17 a of the lubricating oil passage 17 is inclined toward the upstream side in the rotational direction of the oil disk 11 with respect to the radial direction of the oil disk 11.
  • the lubricating oil introduction groove 16 is inclined toward the upstream side in the rotation direction of the oil disk 11, so that the lubricating oil scooped up by the rotating oil disk 11 easily enters the lubricating oil introduction groove 16.
  • the angle of the lubricating oil introduction groove 16 with respect to the radial direction of the oil disk 11 is, for example, in the range of 30 degrees to 60 degrees.
  • the inclination angle of the lubricating oil introduction groove 16 is appropriately set in consideration of operating conditions such as the rotational speed of the rotating shaft 1, physical properties such as the viscosity of the lubricating oil, and the amount of lubricating oil supplied to the thrust bearing unit 9A.
  • the lubricating oil introduction groove 16 may be an arcuate groove having an appropriate curvature radius according to specifications such as operating conditions and physical properties of the lubricating oil.
  • the lubricant introduction groove 16 may be a spiral groove.
  • FIG. 9 is a view showing the inner surface of the guide disk 15B facing the oil disk 11. As shown in FIG. As shown in FIG. 9, the lubricating oil introduction groove 16 is not provided on the inner surface of the guide disk 15B.
  • the lubricating oil that has entered the lubricating oil introduction groove 16 is guided to the lubricating oil passage 17 that communicates with the lubricating oil introduction groove 16.
  • the lubricating oil passage 17 extends to the thrust bearing unit 9A. More specifically, the lubricating oil passage 17 extends from the inner surface of the guide casing 15 in the axial direction of the rotary shaft 1 and further extends in a direction perpendicular to the axial direction of the rotary shaft 1 to reach the thrust bearing unit 9A. Yes.
  • the lubricating oil is supplied to the thrust bearing unit 9A through the lubricating oil passage 17.
  • Circumferential position of the lubricating oil passage 17 and the form of the lubricating oil passage 17 (for example, cross-sectional area, length, passage direction relative to the oil disk rotation direction, flow resistance factors such as surface roughness, or excess provided in the passage
  • the amount of lubricating oil supplied to the thrust bearing unit 9A can be limited to a suitable amount.
  • the lubricating oil passage 17 may be disposed at a position near the rotating shaft 1 that is equal to or smaller than the outer diameter of the oil disk 11.
  • the thrust bearing unit 9 ⁇ / b> A includes two bearings 31 and 32 arranged in series on the rotary shaft 1, and an annular shape arranged between the bearings 31 and 32. And a spacer (spacer) 19.
  • the bearings 31 and 32 angular ball bearings that can receive both the axial load and the radial load of the rotary shaft 1 are used. This angular ball bearing functions as a radial bearing and a thrust bearing.
  • the spacer 19 also functions as a lubricant guide for supplying lubricant to the bearings 31 and 32 evenly. Three or more bearings may be provided. Also in this case, the spacer 19 is disposed between two adjacent bearings.
  • FIG. 10A is a sectional view showing a part of the bearing device along the longitudinal direction of the rotating shaft 1
  • FIG. 10B is a diagram showing a section of the bearing device seen from the longitudinal direction of the rotating shaft 1.
  • a plurality of oil supply holes 18 for efficiently distributing the lubricant supplied from the lubricant passage 17 to the bearings 31 and 32 are provided on the outer periphery of the spacer 19. Each oil supply hole 18 extends from the outer peripheral surface of the spacer 19 to the inner peripheral surface.
  • the diameter and number of the oil supply holes 18 are appropriately set in consideration of operating conditions such as the rotational speed of the rotating shaft 1, physical properties such as the viscosity of the lubricating oil, and the amount of lubricating oil supplied to the thrust bearing unit 9A.
  • the lubricating oil pumped up by the rotation of the oil disk 11 is properly supplied to the thrust bearing unit 9A, a highly reliable self-lubricating bearing device can be configured even at a high peripheral speed. It becomes possible. Specifically, in the past, a peripheral speed of about 14 m / s was the limit of a self-lubricating bearing device. However, according to the present invention, the peripheral speed limit applicable to self-lubrication is 16 to 18 m / s, or It becomes possible to increase to the above peripheral speed.
  • the present invention it is possible to stably supply the lubricating oil to the thrust bearing unit 9A even under high peripheral speed conditions of the rotary shaft 1, which has been difficult to supply by conventional techniques such as an oil ring.
  • the forced oiling device is not required, the installation area of the pump is reduced, and the cost is reduced, so that the product competitiveness in the market can be increased.
  • the oil disk 11 is surrounded by the guide casing 15 disposed opposite to and close to the oil disk 11, it is possible to prevent useless scattering of the lubricating oil pumped up by the oil disk 11. .
  • an amount of lubricating oil more than necessary and sufficient can be guided to the lubricating oil passage 17 that leads to the bearings 31 and 32. Since the lubricating oil passage 17 extends in the axial direction from the inner surface of the oil disk 15, it is possible to provide a bearing device that is more compact than the conventional one without requiring complicated processing.
  • the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the technical idea described in the claims and the specification and drawings. Is possible.
  • the oil disk 11 and the guide casing 15 are provided for supplying the lubricating oil to the thrust bearing unit 9A.
  • the oil disk and the guide for supplying the lubricating oil to the radial bearing unit 9B are provided.
  • a casing may be provided.
  • the axial gap W1 and radial gap W2 between them, the circumferential position and inclination of the lubricant introduction groove 16, the cross-sectional area of the lubricant passage 17, the shape of the spacer 19 disposed between the bearings, and the like are appropriately designed and By selecting, the present invention can be applied to various types of pumps.
  • the present invention relates to a bearing device used for a horizontal shaft pump or the like, and more particularly, to a bearing device capable of appropriately supplying lubricating oil to a bearing even when the diameter of a rotating shaft is increased or the rotational speed is increased. Is available. Further, the present invention can be used for a pump provided with such a bearing device.

Abstract

La présente invention concerne un dispositif de palier qui est plus compact que la technique antérieure et n'exige pas d'usinage compliqué, et avec lequel de l'huile de lubrification peut être alimentée dans une quantité appropriée et d'une manière stable à un palier, même lorsque la vitesse périphérique d'un arbre rotatif est augmentée pour atteindre une vitesse élevée. De plus, la présente invention concerne une pompe équipée d'un tel dispositif de palier. Le dispositif de palier est équipé de : un palier (32) qui reçoit la charge d'un arbre rotatif (1) ; un réservoir d'huile de lubrification (10) disposé sous le palier (32) ; un disque d'huile (11) qui est fixé à, et tourne de façon solidaire avec, l'arbre rotatif (1), ce qui récupère l'huile de lubrification stockée dans le réservoir d'huile de lubrification (10) ; un conduit d'huile de lubrification (17) s'étendant jusqu'au palier (32) ; et un carter de guidage (15) qui guide l'huile de lubrification récupérée par le disque d'huile (11) vers le conduit d'huile de lubrification (17). Le carter de guidage (15) possède une surface interne qui fait face à la surface latérale et à la surface périphérique externe du disque d'huile (11).
PCT/JP2014/084007 2013-12-26 2014-12-23 Dispositif de palier et pompe WO2015098896A1 (fr)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017032115A (ja) * 2015-08-05 2017-02-09 株式会社荏原製作所 軸受装置および回転機械
JP2017032134A (ja) * 2015-08-06 2017-02-09 株式会社荏原製作所 軸受装置および回転機械

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4627930Y1 (fr) * 1968-05-24 1971-09-28
JPS58102824U (ja) * 1981-12-29 1983-07-13 株式会社熊商 軸受間座
JP2006345675A (ja) * 2005-06-10 2006-12-21 Mitsubishi Electric Corp 鉄道車両用駆動電動機
JP2009166787A (ja) * 2008-01-18 2009-07-30 Jtekt Corp 車両用軸受装置
JP2011043207A (ja) * 2009-08-21 2011-03-03 Nsk Ltd 転がり軸受用潤滑装置

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK127759B (da) * 1971-08-13 1973-12-31 Helsingor Skibsvaerft Lejehus til hurtigtgående aksler.
US5591020A (en) * 1994-05-19 1997-01-07 Environamics Corporation Pump oil mister

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4627930Y1 (fr) * 1968-05-24 1971-09-28
JPS58102824U (ja) * 1981-12-29 1983-07-13 株式会社熊商 軸受間座
JP2006345675A (ja) * 2005-06-10 2006-12-21 Mitsubishi Electric Corp 鉄道車両用駆動電動機
JP2009166787A (ja) * 2008-01-18 2009-07-30 Jtekt Corp 車両用軸受装置
JP2011043207A (ja) * 2009-08-21 2011-03-03 Nsk Ltd 転がり軸受用潤滑装置

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017032115A (ja) * 2015-08-05 2017-02-09 株式会社荏原製作所 軸受装置および回転機械
WO2017022517A1 (fr) * 2015-08-05 2017-02-09 株式会社 荏原製作所 Dispositif de palier et machine rotative
JP2017032134A (ja) * 2015-08-06 2017-02-09 株式会社荏原製作所 軸受装置および回転機械

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