WO2015189882A1 - Dispositif de palier lisse - Google Patents

Dispositif de palier lisse Download PDF

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Publication number
WO2015189882A1
WO2015189882A1 PCT/JP2014/065171 JP2014065171W WO2015189882A1 WO 2015189882 A1 WO2015189882 A1 WO 2015189882A1 JP 2014065171 W JP2014065171 W JP 2014065171W WO 2015189882 A1 WO2015189882 A1 WO 2015189882A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing device
rotating shaft
sliding
sliding layer
base metal
Prior art date
Application number
PCT/JP2014/065171
Other languages
English (en)
Japanese (ja)
Inventor
智彬 山下
Original Assignee
株式会社日立製作所
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 株式会社日立製作所 filed Critical 株式会社日立製作所
Priority to PCT/JP2014/065171 priority Critical patent/WO2015189882A1/fr
Publication of WO2015189882A1 publication Critical patent/WO2015189882A1/fr

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    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/03—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/06—Sliding-contact bearings for exclusively rotary movement for axial load only with tiltably-supported segments, e.g. Michell bearings
    • 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
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings

Definitions

  • the present invention relates to a plain bearing device for supporting a high-speed rotating body such as a turbo machine or a rotating electric machine.
  • plain bearings have a structure in which a non-ferrous metal with low strength and low melting point, such as white metal, which is a tin-based alloy, and aluminum alloy is lined on a base metal made of an iron-based alloy or a copper alloy as a sliding material. It has become.
  • resin materials such as polytetrafluoroethylene and polyetheretherketone may be used as the sliding material.
  • Patent Document 1 in a journal slide bearing comprising an upper half bearing and a lower half bearing, a flow path for cooling oil is provided on the back side of the sliding surface of the lower half bearing, A structure that can cool the position is proposed.
  • An object of the present invention is to provide a plain bearing device with improved reliability.
  • the plain bearing device includes a rotating shaft, a base metal that is disposed around the rotating shaft, and a load disposed between the rotating shaft and the base metal. And a sliding layer having a thickness that decreases from the operating position toward the rotational direction.
  • FIG. 6 is a cross-sectional view (a cross-sectional view taken along line AA in FIG. 4) in which a part of the bearing portion of the tilting pad thrust bearing device including the embodiment of the present invention is developed linearly (embodiment 3).
  • Example 4 which is a perspective view of the taper thrust bearing apparatus provided with the Example of this invention.
  • Example 4 which is a top view of the taper thrust bearing apparatus provided with the Example of this invention.
  • FIG. 9 is a cross-sectional view (a cross-sectional view taken along line AA in FIG. 7) in which a part of the bearing portion of the taper thrust bearing device including the embodiment of the present invention is linearly developed (Example 4).
  • FIG. 6 is a circumferential distribution diagram of oil film pressure and temperature on a bearing sliding surface. It is the schematic which showed the form of the creep deformation
  • FIG. 9 a schematic diagram of the circumferential distribution of oil film pressure and temperature in a cylindrical plain bearing is shown.
  • both temperature and pressure are distributed, and the temperature peak tends to be delayed with respect to the rotation direction than the pressure peak.
  • Such distribution is not limited to the cylindrical slide bearing, but is the same in the tilting pad radial bearing and the thrust bearing.
  • a region 4 surrounded by a broken line in FIG. 9 is a region where both the temperature and the pressure are high.
  • the sliding material may be creep-deformed in the concave direction. Since the creep deformation is a constant volume deformation, the volume deformed in the concave direction by the oil film pressure flows and is pushed out to the low oil film pressure side.
  • the bearing sliding surface as shown in FIG. Becomes a wavy shape.
  • the sliding layer is provided so that the thickness decreases from the load acting position toward the rotation direction side (in a direction substantially perpendicular to the rotation axis).
  • the thickness of the sliding layer in the vicinity of the region 4 where the possibility of creep deformation is high is reduced.
  • the load application position corresponds to the support part serving as a fulcrum when tilting with the support part of the base metal by the support part (pivot position) during operation, and corresponds to the lowermost part in the vertical direction due to gravity when it does not tilt. . It is sufficient that the lowermost portion is substantially the lowermost portion, and the lowermost portion does not have to be strictly the lowermost portion.
  • FIG. 1 shows a cross-sectional view of the first embodiment of the present invention during operation.
  • the present embodiment relates to a cylindrical plain bearing device.
  • the bearing of this example has a two-part structure of an upper half 12 and a lower half 13.
  • a sliding layer 2 is lined on a base metal 3 made of an iron-based alloy or a copper alloy.
  • a non-ferrous metal such as a white alloy, an aluminum alloy, or a copper alloy that is a tin-based alloy, or a resin material such as polytetrafluoroethylene or polyetheretherketone may be used.
  • an external oil supply system not shown.
  • the thickness of the sliding layer 2 becomes thinner from the load acting point 14 of the rotating shaft 1 as it advances in the direction of rotation.
  • the position where the thickness of the sliding layer is the thinnest is located within 0 to 90 degrees from the load application position toward the rotation direction.
  • the sliding layer 2 of the upper half 12 is not shown, but the sliding layer 2 thicker than the region 4 may be present in the upper half.
  • FIG. 9 shows the oil film pressure distribution and oil film temperature distribution during operation.
  • the lubricating oil flows into the wedge-shaped gap between the sliding layer 2 and the rotating shaft 1 to form an oil film and generate pressure, thereby causing the rotating shaft 1 to float.
  • the center of the rotating shaft 1 is decentered in the direction of rotation so that the vertical component of the oil film pressure and the load of the rotating shaft 1 are balanced. Therefore, the oil film pressure has a distribution as shown in FIG.
  • the position where the oil film pressure / temperature becomes maximum is a region 4 surrounded by a broken line in FIG.
  • the sliding layer may creep in the concave direction.
  • the creep deformation is a constant volume deformation
  • the volume deformed in the concave direction by the oil film pressure flows and is pushed out to the low oil film pressure side, and the sliding surface as shown in FIG. Shape.
  • the amount of deformation due to creep is large, the sliding surface shape becomes non-uniform and the oil film is not formed properly, which may affect the bearing performance.
  • the thickness of the sliding layer in the vicinity of the region 4 where the possibility of creep deformation is high is small, the volume of the sliding layer 2 is small, and the amount of creep deformation can be reduced. Than this. It is possible to keep the sliding surface shape in a uniform state, and an appropriate oil film can be secured.
  • FIG. 2 shows a cross-sectional view of the second embodiment of the present invention during operation.
  • Examples 2 and 3 relate to a tilting pad bearing in which the pad is inclined during operation.
  • a stand 7 is provided so as to surround the base 3.
  • the pivot 5 (equivalent to a support part) which is arrange
  • the base 3 is supported so as to be tiltable with respect to the gantry 7.
  • the present invention is applied to a tilting pad radial bearing device.
  • the base metal 3 is disposed on one surface of the gantry 7 with a (fixed) interval in the circumferential direction.
  • the base metal 3 is divided into a plurality in the rotational direction.
  • a plurality of pads 6 having a sliding layer 2 lined on the surface of the base metal 3 on the rotating shaft 1 side are formed on a base metal 3 made of an iron-based alloy or a copper alloy by a pivot 5 arranged on the base 7. Supported and tiltable.
  • the material of the sliding layer 2 is the same as that of the first embodiment.
  • the thickness of the sliding layer 2 provided with each pad 6 decreases (for example, monotonously) in the direction of rotation of the rotary shaft 1 in each pad 6.
  • the tilting pad radial bearing can tilt with the pivot 5 as a fulcrum, and as shown in FIG. 2, during operation, the gap between the rotating shaft 1 and the pad 6 of the pad 6 becomes narrower as it advances in the rotating direction. Tilt.
  • the pressure of the oil film and the temperature of the oil film are maximized in a region 4 surrounded by a broken line in FIG. 2, and the possibility of creep deformation in this region is high.
  • the creep deformation amount in the region 4 is small because the thickness of the sliding layer 2 is small in the vicinity of the region 4 as in the first embodiment. As a result, the sliding surface shape can be maintained in a uniform state, and an appropriate oil film can be secured.
  • FIG. 3 is a perspective view of the third embodiment of the present invention
  • FIG. 4 is a top view thereof
  • FIG. 5 is a sectional view taken along line AA in FIG.
  • FIG. 5 shows a disc-shaped thrust runner 8 not shown in FIG.
  • the thrust runner 8 has a disk shape, and has a disk shape.
  • the present invention is applied to a tilting pad thrust bearing device.
  • the base metal 3 is divided into a plurality in the rotational direction.
  • a plurality of pads 6 in which a sliding layer 2 is lined on the surface on the rotating shaft 1 side are supported on a base 3 made of an iron-based alloy or a copper alloy by pivots 5 arranged on the base 7 in the circumferential direction. And can be tilted.
  • the material of the sliding layer 2 is the same as that of the first embodiment.
  • Lubricating oil supplied from an external oil supply system exists between the disc-shaped thrust runner 8 and the sliding layer 2 attached to the rotary shaft 1. Further, the thickness of the sliding layer 2 provided with each pad 6 decreases (for example, monotonously) in the direction in which the thrust runner 8 rotates.
  • the pads 6 can be tilted with the pivot 5 as a fulcrum, and each pad 6 is tilted in the direction of rotation so that the gap between the thrust runner 8 and the pad 6 is narrowed.
  • the pressure of the oil film and the temperature of the oil film are maximized in the region 4 surrounded by the broken line in FIG. 5, and the possibility of creep deformation in this region is high.
  • the thickness of the sliding layer 2 is reduced in the vicinity of the region 4 for each base metal, so that the amount of creep deformation is reduced. Therefore, the uniformity of the sliding surface shape can be maintained, and an appropriate oil film can be secured.
  • FIG. 6 is a perspective view of the form of the fourth embodiment of the present invention
  • FIG. 7 is a top view thereof
  • FIG. 8 is a sectional view taken along line AA in FIG.
  • FIG. 8 shows a disc-shaped thrust runner 8 not shown in FIG.
  • the present invention is applied to a taper thrust bearing device.
  • Each of a plurality of base metals 3 made of an iron-based alloy or a copper alloy is provided with a taper portion 9 in which a sliding layer 2 is lined on the surface on the rotating shaft 1 side.
  • the taper portion 9 is shaped so as to approach the thrust runner 8 as it advances in the rotational direction, and the material of the sliding layer 2 is the same as in the first embodiment.
  • Lubricating oil supplied from an external oil supply system (not shown) exists between the disk-shaped thrust runner 8 attached to the rotary shaft 1 and the sliding layer 2.
  • the shape of the taper portion 9 is inclined so that the gap with the thrust runner 8 becomes narrower in the direction of rotation, and the thickness of the sliding layer 2 of each taper portion 9 is determined by the thrust runner. It decreases (for example, monotonously) toward the rotation direction of 8.
  • the function and effect of this embodiment will be described.
  • the taper portion 9 is inclined so as to narrow the gap with the thrust runner 8 as the rotating shaft 1 advances in the rotational direction, an oil film pressure due to the wedge effect is generated.
  • the pressure of the oil film and the temperature of the oil film are maximized in a region 4 surrounded by a broken line in FIG. 8, and there is a high possibility of creep deformation in this region.
  • the present embodiment is the same as the first to third embodiments, and the thickness of the sliding layer 2 is reduced in the vicinity of the region 4 for each base metal, so that the amount of creep deformation in the region 4 is reduced. Therefore, the uniformity of the sliding surface shape can be maintained, and an appropriate oil film can be secured.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

　Le but de l'invention consiste à produire un dispositif de palier lisse ayant une fiabilité améliorée. Pour résoudre ce problème, le dispositif de palier lisse est caractérisé en ce qu'il comprend un arbre rotatif (1), un métal de base (3) disposé autour de l'arbre rotatif (1) et une couche de glissement (2) agencée entre l'arbre rotatif (1) et le métal de base (3) et diminuant l'épaisseur le long de la direction de rotation depuis une position d'application de charge.
PCT/JP2014/065171 2014-06-09 2014-06-09 Dispositif de palier lisse WO2015189882A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2014/065171 WO2015189882A1 (fr) 2014-06-09 2014-06-09 Dispositif de palier lisse

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2014/065171 WO2015189882A1 (fr) 2014-06-09 2014-06-09 Dispositif de palier lisse

Publications (1)

Publication Number Publication Date
WO2015189882A1 true WO2015189882A1 (fr) 2015-12-17

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PCT/JP2014/065171 WO2015189882A1 (fr) 2014-06-09 2014-06-09 Dispositif de palier lisse

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WO (1) WO2015189882A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0571538A (ja) * 1991-09-12 1993-03-23 Ndc Co Ltd 半割軸受
JPH07332364A (ja) * 1994-02-21 1995-12-22 Miba Gleitlager Ag 動液圧滑り軸受
JPH10103345A (ja) * 1996-09-30 1998-04-21 Mitsubishi Heavy Ind Ltd スラスト軸受装置
JP2000018253A (ja) * 1998-06-29 2000-01-18 Daido Metal Co Ltd すべり軸受
JP2002106552A (ja) * 2000-09-28 2002-04-10 Hitachi Engineering & Services Co Ltd スラスト軸受装置及びその製造方法
JP2004197890A (ja) * 2002-12-20 2004-07-15 Hitachi Ltd ティルティングパッド軸受装置
JP2014503759A (ja) * 2010-11-24 2014-02-13 マーレ インターナショナル ゲゼルシャフト ミット ベシュレンクテル ハフツング 一体化されたシールを備える軸受

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0571538A (ja) * 1991-09-12 1993-03-23 Ndc Co Ltd 半割軸受
JPH07332364A (ja) * 1994-02-21 1995-12-22 Miba Gleitlager Ag 動液圧滑り軸受
JPH10103345A (ja) * 1996-09-30 1998-04-21 Mitsubishi Heavy Ind Ltd スラスト軸受装置
JP2000018253A (ja) * 1998-06-29 2000-01-18 Daido Metal Co Ltd すべり軸受
JP2002106552A (ja) * 2000-09-28 2002-04-10 Hitachi Engineering & Services Co Ltd スラスト軸受装置及びその製造方法
JP2004197890A (ja) * 2002-12-20 2004-07-15 Hitachi Ltd ティルティングパッド軸受装置
JP2014503759A (ja) * 2010-11-24 2014-02-13 マーレ インターナショナル ゲゼルシャフト ミット ベシュレンクテル ハフツング 一体化されたシールを備える軸受

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