WO2013002142A1 - ターボチャージャの軸受装置 - Google Patents

ターボチャージャの軸受装置 Download PDF

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Publication number
WO2013002142A1
WO2013002142A1 PCT/JP2012/066000 JP2012066000W WO2013002142A1 WO 2013002142 A1 WO2013002142 A1 WO 2013002142A1 JP 2012066000 W JP2012066000 W JP 2012066000W WO 2013002142 A1 WO2013002142 A1 WO 2013002142A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
floating bush
peripheral surface
housing
floating
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2012/066000
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
西田　英朗
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
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 Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Priority to EP12803917.9A priority Critical patent/EP2728212B1/en
Priority to CN201280027265.XA priority patent/CN103597227B/zh
Priority to US14/125,810 priority patent/US9587515B2/en
Publication of WO2013002142A1 publication Critical patent/WO2013002142A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F01D25/166—Sliding contact bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/18—Lubricating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/18—Lubricating arrangements
    • F01D25/22—Lubricating arrangements using working-fluid or other gaseous fluid as lubricant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F02B39/14—Lubrication of pumps; Safety measures therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • 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
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/18—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with floating brasses or brushing, rotatable at a reduced speed
    • 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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/02—Sliding-contact bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/50—Bearings
    • F05D2240/54—Radial bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/60—Structure; Surface texture
    • F05D2250/61—Structure; Surface texture corrugated
    • 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
    • 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
    • F16C17/26—Systems consisting of a plurality of sliding-contact 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
    • F16C2202/00—Solid materials defined by their properties
    • F16C2202/50—Lubricating properties
    • F16C2202/54—Molybdenum disulfide
    • 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
    • F16C2206/00—Materials with ceramics, cermets, hard carbon or similar non-metallic hard materials as main constituents
    • F16C2206/02—Carbon based material
    • F16C2206/04—Diamond like carbon [DLC]
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/23—Gas turbine engines
    • F16C2360/24—Turbochargers
    • 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
    • F16C33/043—Sliding surface consisting mainly of ceramics, cermets or hard carbon, e.g. diamond like carbon [DLC]
    • 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
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid

Definitions

  • the present invention relates to a floating bush bearing suitable for a rotating machine having a high-speed rotating shaft such as a turbocharger.
  • the floating bush In the floating bush bearing, the floating bush is rotatably interposed in a gap between the rotating shaft and the bearing housing, and pressurized lubricating oil supplied from the bearing housing is supplied between the inner peripheral surface of the bearing housing and the outer peripheral surface of the floating bush.
  • the oil is supplied to the gap between the inner peripheral surface of the floating bush and the rotary shaft by a radial oil supply passage provided in the floating bush. And it is comprised so that it may support stably while suppressing the vibration of a rotating shaft by the damping effect of the lubricating oil film formed in these gaps, and may prevent seizure.
  • FIG. 5 shows a detailed view of a floating bush bearing that rotatably supports a rotating shaft of a high-speed rotating machine such as a turbocharger.
  • a turbocharger 0100 includes a pair of impellers 0102a and 0102b and a rotor shaft 0104 that integrally connects them.
  • the floating bush bearing 0110 includes a bearing housing 0112 and a floating bush 0114 that is interposed between the bearing housing 0112 and the rotor shaft 0104 and supports the rotor shaft 0104 in a rotatable manner.
  • Oil passages 0116 and 0118 are provided in the bearing housing 0112 and the floating bush 0114, respectively. Then, the lubricating oil passes through the oil passages 0116 and 0118 from the bearing housing 0112, and the clearance between the inner peripheral surface of the bearing housing 0112 and the outer peripheral surface of the floating bush 0114 and the clearance between the inner peripheral surface of the floating bush 0114 and the rotor shaft 0104. To be supplied.
  • the floating bush 0114 is rotatably arranged and rotates at a slower speed than the rotor shaft 0104 due to sliding resistance with the rotor shaft 0104.
  • the lubricating oil forms an oil film in these gaps, thereby preventing seizure and damage (abrasion) occurring on the sliding surfaces of the gaps.
  • Patent Document 1 JP 2009-156333 A (Patent Document 1), by making the inner bearing width Lc of the compressor side floating bush bearing smaller than the inner bearing width Lt of the turbine side floating bush bearing (Lc ⁇ Lt), The spring constant due to the oil film that the compressor side floating bush bearing has is smaller than the spring constant due to the oil film that the turbine side floating bush bearing has. The balance is maintained between the side floating bush bearing and the compressor side floating bush bearing, and the natural frequency in the self-excited vibration in the high frequency range is lowered, thereby reducing noise.
  • Patent Document 2 Japanese Patent Application Laid-Open No. 2007-46642 (Patent Document 2), a spiral groove is provided on at least one of the inner peripheral surface and the outer peripheral surface of the full float bearing, and when the full float bearing rotates, the inner peripheral surface and the outer peripheral surface are rotated.
  • the distribution of pressure that the inner peripheral surface and the outer peripheral surface receive from the fluid (lubricating oil) changes along the axial direction by the spiral groove provided in at least one of the above. Due to this change, the full float bearing is unlikely to be in a stable state, and self-excited vibration is suppressed.
  • the internal vibration width Lc of the compressor side floating bush bearing is made smaller than the inner bearing width Lt of the turbine side floating bush bearing (Lc ⁇ Lt), so that the natural vibration in the self-excited vibration in the high frequency range is obtained.
  • the noise is reduced by reducing the number, but the shape of the compressor side floating bush bearing and the turbine side floating bush bearing is different, so the number of parts increases, management costs increase, and there is a risk of misassembly. Has a defect that becomes higher.
  • it is the structure where the spiral groove is provided in at least one of the internal peripheral surface and outer peripheral surface of a full float bearing. Accordingly, the machining of the groove, particularly the groove provided on the inner peripheral surface, is complicated because the inner diameter of the portion into which the rotor shaft of the turbine rotor is fitted is complicated, increasing the number of processing steps and increasing the cost of the parts. .
  • the present invention has been made in view of such problems, and the first floating bush bearing disposed on the compressor housing side and the second floating bush bearing disposed on the turbine housing side have substantially the same shape.
  • the inner bearing width Li is smaller than the outer bearing width Lo of each floating bush bearing by the same ratio in both the first floating bush and the second floating bush, thereby improving the vibration stability at the time of high rotation of the turbine rotor.
  • the object is to facilitate the processing and assembly by reducing the number of parts.
  • the present invention achieves such an object, and a bearing housing interposed between a turbine housing and a compressor housing of a turbocharger that pressurizes supply air to a combustion chamber of an internal combustion engine, and penetrates through the bearing housing.
  • An oil supply passage that is interposed between the rotor shaft of the turbine rotor, the bearing housing, and the rotor shaft and that communicates the outer peripheral surface and the inner peripheral surface is provided, and the lubricating oil from the bearing housing is disposed on the outer peripheral surface.
  • a first floating bush bearing provided on the compressor housing side that is supplied to the inner peripheral surface and having a first floating bush, and a second floating bush bearing that is disposed on the turbine housing side in the same shape as the first floating bush bearing.
  • a second floating bush bearing with a floating bush; Both the first and second floating bushes are characterized in that the inner bearing width Li is smaller than the outer bearing width Lo at the same ratio.
  • the inner bearing width Li of each of the first and second floating bushes smaller than the outer bearing width Lo, the amount of rotation of each floating bush bearing at the time of high-speed rotation of the rotor shaft can be reduced, and high-speed rotation can be achieved. Improves vibration stability at the time and obtains noise reduction effect. Further, since the ratio between the inner bearing width and the outer bearing width of each of the first and second floating bushes is the same, the viscosity resistance of the lubricating oil generated in the first and second floating bushes becomes the same, and the rotor shaft The spindle is stable.
  • each of the first and second floating bushes has the same shape, the number of parts can be reduced to facilitate processing and assembly, reduce the risk of erroneous assembly, and stabilize the processing quality and reduce the cost. . Further, the damping effect between the floating bush bearing and the housing can be maintained by making the outer bearing width larger than the inner one.
  • the required minimum bearing width on the inner circumference side including the lubricating oil passage diameter ⁇ is Lx
  • the ratio Li / Lo between the outer bearing width Lo and the inner bearing width Li is in the following range. It is good to set to satisfy. Lx / Lo ⁇ Li / Lo ⁇ 0.5 (1)
  • the amount of rotation of each floating bush during high-speed rotation of the rotor shaft is maintained at an appropriate number of rotations relative to the number of rotations of the rotor shaft, and the stability of rotational vibration is improved and noise reduction effect is achieved.
  • the width on the minimum side is made smaller than the communication hole ⁇ , the tip of the oil supply passage is scraped by the conical inclined surface, and the lubricating oil flows directly from the communication hole ⁇ in the axial direction of the rotor shaft. The damping effect of lubricating oil with the rotor shaft is halved.
  • the outer peripheral surface of the floating bush is provided with a low friction treatment.
  • DLC Diamond Like Carbon
  • molybdenum disulfide a solid lubricant containing molybdenum disulfide is coated on the bearing outer peripheral surface of the floating bush.
  • a surface texture (dimple or minute recess) is formed on the outer peripheral surface of the bearing of the floating bush.
  • the low-friction treatment is performed by arranging a groove communicating with the oil supply hole on the outer peripheral surface of the floating bush.
  • the lubricating oil sent from the lubricating oil passage flows to the lower side of the floating bush through the end groove and fills the space between the floating bush and the bearing housing with the lubricating oil.
  • the first and second floating bushes have inner bearing widths smaller than the respective outer bearing widths, so that the amount of rotation of the respective floating bushes during high-speed rotation of the rotor shafts can be determined.
  • the rotation speed is maintained at an appropriate value, and the stability of rotational vibration is improved to obtain a noise reduction effect.
  • the rotor shaft can maintain the damping effect between the floating bush bearing and the housing by making the outer bearing width larger than the inner one. Since each of the first and second floating bushes has the same shape, the number of parts can be reduced to facilitate processing and assembly, reduce the risk of erroneous assembly, and stabilize the processing quality and reduce the cost. .
  • FIG. 1 shows a first embodiment of a low friction process provided on the outer periphery of a floating bush. These show the second embodiment of the low friction treatment provided on the outer periphery of the floating bush.
  • C1 shows a third embodiment of the low friction treatment provided on the outer periphery of the floating bush, and (C2) shows a longitudinal sectional view in the radial direction of (C1).
  • D1) shows a fourth embodiment of a low friction process provided on the outer periphery of the floating bush, and (D2) shows a longitudinal sectional view in the radial direction of (D1). Shows an explanatory diagram of the prior art.
  • FIG. 1 is a detailed view of a floating bush bearing that rotatably supports high-speed rotation of a turbocharger embodying the present invention.
  • a turbocharger 1 is supplied to an engine by an exhaust turbine 14 driven by exhaust gas of an internal combustion engine (hereinafter referred to as “engine”), a turbine housing 11 covering the exhaust turbine 14, and a driving force of the exhaust turbine 14.
  • engine an internal combustion engine
  • a compressor impeller 15 that pressurizes the supply air, a compressor housing 12 that covers the compressor impeller 15, a rotor shaft 16 that integrally connects the exhaust turbine 14 and the compressor impeller 15, a turbine housing 11 and the compressor housing 12, And a bearing housing 13 that supports the rotor shaft 16, a thrust bearing 16 b that receives the thrust load of the rotor shaft 16, and tightening by a fastening member (not shown) from the compressor impeller 15 side.
  • Compressor impeller 15 It is constituted by a sleeve 16c which the determining.
  • the bearing housing 13 is provided with a first floating bush bearing 17 that supports the rotor shaft 16 on the compressor impeller 15 side, and a second floating bush bearing 18 that supports the exhaust turbine 14 side.
  • the first floating bush bearing 17 includes a bearing portion 13d formed in the bearing housing 13 and a first floating bush 19 that is fitted in the bearing portion 13d and in which the rotor shaft 16 is disposed.
  • the first floating bush 19 is formed in an annular shape, and is provided with an oil supply passage 19a penetrating from the outer peripheral surface to the inner peripheral surface.
  • the second floating bush bearing 18 includes a bearing portion 13d formed in the bearing housing 13 and a second floating bush 20 that is fitted in the bearing portion 13d and in which the rotor shaft 16 is disposed. ing.
  • the second floating bush 20 is formed in an annular shape, and is provided with an oil supply passage 20a penetrating from the outer peripheral surface to the inner peripheral surface.
  • Lubricating oil is fed to the floating bush bearings 17 and 18 through a pipe (not shown) connected to the connection port 13a of the bearing housing 13.
  • the compressor side lubricating oil passage 13c is an oil passage inclined linearly from the connection port 13a toward the first floating bush bearing 17 side.
  • the lubricating oil sent to the first floating bush bearing 17 side is also sent to the first floating bush bearing 17 and between the first floating bush bearing 17 and the thrust bearing 16b, and the lubrication of the part is performed. Cooling is in progress.
  • the turbine side lubricating oil passage 13b is an oil passage inclined linearly from the connection port 13a to the second floating bush bearing 18 side, and the lubricating oil fed to the second floating bush bearing 18 side is Oil is fed to the second floating bush bearing 18 and the enlarged diameter portion 16d of the rotor shaft 16 on the exhaust turbine 14 side to lubricate and cool the portion.
  • the lubricating oil sent to the first floating bush bearing 17 fills the gap between the bearing portion 13d and the first floating bush 19 and passes through the oil supply passage 19a penetrating from the outer peripheral side of the first floating bush 19 to the inner peripheral side. As shown, the first floating bush 19 and the support shaft portion 16a of the rotor shaft 16 are supplied.
  • the lubricating oil fed to the second floating bush bearing 18 fills the gap between the bearing portion 13d and the second floating bush 20 and passes through an oil supply passage 20a penetrating from the outer peripheral side of the second floating bush 20 to the inner peripheral side.
  • the second floating bush 20 is supplied between the second floating bush 20 and the support shaft portion 16a of the rotor shaft 16.
  • Each of the floating bushes 19 and 20 and the rotor shaft 16 is floatingly supported on the bearing housing 13 by an oil film of lubricating oil.
  • the first floating bush bearing 17 including the first floating bush 19
  • the second floating bush bearing 18 including the second floating bush 20
  • the “first floating bush bearing 17” and the “first floating bush 19” will be representatively described as the “floating bush bearing 17” and the “floating bush 19” in order to avoid duplication of explanation.
  • FIG. 2 shows the floating bush bearing 17 of the present invention, which will be described with reference to FIG.
  • the floating bush 19 constituting the floating bush bearing 17 is disposed so as to have a gap ⁇ for forming an oil film between the bearing portion 13 d of the bearing housing 13 and the outer peripheral surface 19 b of the floating bush 19.
  • Lubricating oil is pumped into the gaps ⁇ and ⁇ through the compressor side lubricating oil passage 13c (same as the turbine side lubricating oil passage 13b) in the bearing housing 13.
  • the lubricating oil passes through the oil supply passage 19a of the floating bush 19 while filling the clearance ⁇ , fills the clearance ⁇ between the inner peripheral surface 19c of the floating bush 19 and the support shaft portion 16a, and the rotor shaft 16 floats due to the oil film of the lubricating oil. It is supported by the state.
  • the inner peripheral bearing width Li of the inner peripheral surface of the floating bush 19 is smaller than the outer peripheral bearing width Lo of the outer peripheral surface of the outer peripheral surface.
  • the inner peripheral bearing width Li of the inner peripheral surface 19c of the floating bush 19 is formed by conic cutting both ends of the floating bush 19 from the outside to the inside. In the case of this embodiment, the cutting amounts at both ends are the same, and both ends are symmetrical about the oil supply passage 19a. By making it symmetrical, the uniformity of the distance between the bearing width portion around the oil supply passage 19a on the inner peripheral surface of the floating bush 19 and the support shaft portion 16a is maintained, and the stability of the support shaft is improved.
  • the minimum required bearing width on the inner peripheral side including the diameter ⁇ (lubricating oil path diameter ⁇ ) of the oil supply passage 19a is Lx.
  • the required minimum bearing width Lx is the minimum bearing width for forming an oil film necessary for supporting the support shaft portion 16a on the inner peripheral surface 19c.
  • Lx (required minimum bearing width) required minimum contact width + diameter ⁇ of the oil supply passage 19a is affected by the weight, rotational balance, etc. of the exhaust turbine 14, the compressor impeller 15, and the rotor shaft 16; You just have to decide.
  • FIG. 3 shows an experimental result of a damping ratio% representing the stability of the support shaft of the rotor shaft 16 with respect to the inner / outer width ratio Li / Lo of the floating bush 19.
  • the horizontal axis represents the inner / outer width ratio Li / Lo
  • the vertical axis represents the damping ratio% as a parameter representing the damping characteristic of the oil film.
  • a higher damping ratio indicates better support stability of the rotor shaft 16.
  • the inner bearing width Li of the floating bush 19 is set to the outer bearing. It was smaller than the width Lo. (Test case 1 in Fig. 3)
  • the optimum range of the inner / outer width ratio Li / Lo has been found from the results of this experiment.
  • the inner / outer width ratio Li / Lo of the floating bush 19 is set to Lx / Lo ⁇ Li / Lo ⁇ 0.5.
  • the bearing width Li of the inner peripheral surface 19c is set to Lx as the minimum bearing width necessary for forming the oil diameter and the hole diameter ⁇ of the oil supply passage 19a.
  • the floating bush 19 is formed so as to satisfy Lx / Lo ⁇ Li / Lo ⁇ 0.5, the amount of rotation of the floating bush 19 in the high-speed rotation region of the rotor shaft 16 is optimized. . Accordingly, when the rotor shaft 16 rotates at high speed, the rotation force applied to the floating bush 19 is optimized, and the rotation amount (rotation amount) is reduced (optimized) to reduce the main rotation bearing sliding surface by the rotor shaft 16. Becomes an oil film between the inner peripheral surface 19c of the floating bush 19 and the rotor shaft 16, thereby reducing rotational sliding resistance and vibration of the rotor shaft 16 and improving stability of rotational vibration of the rotor shaft 16. it can.
  • the turbocharger 1 has performance improvement effects such as durability, boost pressure improvement and vibration noise reduction.
  • the ratio of the outer peripheral bearing width Lo of the floating bush 19 to the inner peripheral shaft width Li was set to Lx / Lo ⁇ Li / Lo ⁇ 0.5.
  • the turbocharger rotates at a low speed, it is effective to start the floating bush 19 in an early stage. Therefore, it is necessary to reduce the rotational resistance of the rotor shaft 16 and improve the startup performance of the turbocharger 1.
  • FIG. 4A shows a first embodiment in which low-friction processing is performed, and low-friction processing is provided on the outer peripheral portion of the floating bush 19 so that the floating bush 19 can be quickly started in the low rotation region of the rotor shaft 16.
  • FIG. A DLC (Diamond Like Carbon) coating 19d which is a low friction process, is applied to the outer peripheral surface of the floating bush 19.
  • DLC diamond Like Carbon
  • metal containing DLC WC; tungsten carbide, Si; silicon
  • hydrogen containing DLC As a method for forming DLC, chemical vapor deposition (CVD) is often used, but it is not particularly limited.
  • Cr (chromium) and CrN (chromium nitride) are used as base materials between the base material (floating bush) and the DLC film in order to improve adhesion to the base material (floating bush).
  • Titanium (Ti), titanium nitride (TiN), tungsten carbide (WC), tungsten (W), nickel (Ni), copper (Cu), iron (Fe), iron nitride (FeN), silicon (Si), and Silicon carbide (SiC) or the like may be used as a single layer or a combination of a plurality of layers.
  • the base material itself may be nitrided and used as a base material.
  • the floating bush 19 By making the outer peripheral surface of the floating bush 19 low-friction treatment 19d (for example, DLC coating), the sliding resistance between the oil film interposed between the bearing portion 13d and the outer peripheral surface is reduced. Accordingly, the floating bush 19 is caused to rotate with a relatively low rotation speed (early) of the rotor shaft 16 so that the rotational resistance between the floating bush 19 and the rotor shaft 16 is reduced even when the turbocharger 1 is in the low speed rotation range. Thus, the effect of improving the supercharging pressure of the turbocharger 1 can be obtained.
  • the outer peripheral surface of the floating bush 19 low-friction treatment 19d (for example, DLC coating)
  • FIG. 4B shows a second embodiment of the low friction treatment, in which a dimple 27a is provided on the outer peripheral surface of the floating bush 27 as a low friction treatment.
  • Lubricating oil is held in the concave portion of the dimple 27a, and the bearing portion 13d is contacted.
  • the sliding resistance between the oil film and the outer peripheral surface interposed therebetween is reduced.
  • the dimple 27a can be formed by, for example, a fine particle shot, but is not limited thereto.
  • a hemispherical dimple is used, but there is no particular limitation as long as it has a shape such as a triangular pyramid that allows the dimple portion to hold lubricating oil and reduce the friction coefficient.
  • FIG. 4C (C1) shows a third embodiment of the low friction treatment of the floating bush 30, and FIG. 4C (C2) shows a longitudinal section in the radial direction of (C1).
  • the floating bush 30 is provided with a central groove 30d that is communicated with the oil supply hole 30c penetrating from the outer peripheral surface 30a to the inner peripheral surface 30b at the center of the bearing width of the outer peripheral surface 30a of the floating bush 30 over the entire circumference. .
  • the lubricating oil fed from the lubricating oil passage 13c flows to the lower side of the floating bush 30 through the central groove 30d, and passes between the floating bush 30 and the bearing portion 13d. Filling with lubricating oil reduces the frictional resistance when the floating bush 30 starts rotating.
  • FIG. 4D (D1) shows a fourth embodiment of the low-friction process
  • FIG. 4D (D2) shows a longitudinal section in the radial direction of (D1).
  • the floating bush 35 is provided with an oil supply hole 35c penetrating from the outer peripheral surface 35a to the inner peripheral surface 35b at the approximate center of the bearing width of the outer peripheral surface 35a of the floating bush 35.
  • Two end grooves 35d and 35d are formed over the entire circumference with the oil supply hole 35c of the outer peripheral surface 35a sandwiched in the bearing width direction.
  • a transverse groove 35e that communicates the end grooves 35d, 35d and the oil supply hole 35c is provided for each oil supply hole 35c. Then, as shown in FIG.
  • the lubricating oil fed from the lubricating oil passage 13c flows to the lower side of the floating bush 35 through the end grooves 35d and 35d (arrow), and the floating bush 35 and the bearing portion.
  • the frictional resistance when the floating bush 30 starts rotating is reduced.
  • the amount of rotation of the floating bush during high-speed rotation can be reduced, improving the stability of rotational vibration and reducing noise. Get the effect.
  • the sliding resistance of the rotor shaft 16 during low speed rotation can be improved.
  • the floating bush 19 (20) has the same ratio of the inner bearing width Li and the outer bearing width Lo, the viscosity resistance of the lubricating oil is the same, the support shaft of the rotor shaft 16 is stabilized, and the floating bush 19 (25) is eliminated, the quality is stabilized, and the cost can be reduced.
  • the ratio Li / Lo between the outer bearing width Lo and the inner bearing width Li is set to Lx / Lo ⁇ Li / Lo ⁇ 0.5, whereby the floating bush 19 (20) is rotated with respect to the rotational speed of the rotor shaft 16. Since the rotational speed is optimized, the amount of rotation of each floating bush at the time of high-speed rotation of the rotor shaft can be reduced, the stability of rotational vibration can be improved, and the noise reduction effect can be obtained.
  • a turbocharger that is suitable as a bearing for a rotating shaft that rotates at high speed, can maintain a good supply of lubricating oil to the inner peripheral surface of the floating bush at a simple and low cost, and reduces noise and rotational resistance by stably supporting the rotating shaft. Applicable to any rotating machine.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Sliding-Contact Bearings (AREA)
  • Supercharger (AREA)
PCT/JP2012/066000 2011-06-30 2012-06-22 ターボチャージャの軸受装置 Ceased WO2013002142A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP12803917.9A EP2728212B1 (en) 2011-06-30 2012-06-22 Bearing device for turbocharger
CN201280027265.XA CN103597227B (zh) 2011-06-30 2012-06-22 涡轮增压器的轴承装置
US14/125,810 US9587515B2 (en) 2011-06-30 2012-06-22 Bearing device for turbocharger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011-145797 2011-06-30
JP2011145797A JP5705665B2 (ja) 2011-06-30 2011-06-30 ターボチャージャの軸受装置

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WO2013002142A1 true WO2013002142A1 (ja) 2013-01-03

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US (1) US9587515B2 (enExample)
EP (1) EP2728212B1 (enExample)
JP (1) JP5705665B2 (enExample)
CN (1) CN103597227B (enExample)
WO (1) WO2013002142A1 (enExample)

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CN103597227B (zh) 2016-04-13
JP5705665B2 (ja) 2015-04-22
US9587515B2 (en) 2017-03-07
EP2728212B1 (en) 2020-10-14
EP2728212A4 (en) 2015-03-11
JP2013011331A (ja) 2013-01-17
EP2728212A1 (en) 2014-05-07
CN103597227A (zh) 2014-02-19
US20140119898A1 (en) 2014-05-01

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