WO2013145078A1 - Exhaust turbine supercharger - Google Patents

Exhaust turbine supercharger Download PDF

Info

Publication number
WO2013145078A1
WO2013145078A1 PCT/JP2012/057734 JP2012057734W WO2013145078A1 WO 2013145078 A1 WO2013145078 A1 WO 2013145078A1 JP 2012057734 W JP2012057734 W JP 2012057734W WO 2013145078 A1 WO2013145078 A1 WO 2013145078A1
Authority
WO
WIPO (PCT)
Prior art keywords
edge
introduction hole
deflector
exhaust turbine
turbine supercharger
Prior art date
Application number
PCT/JP2012/057734
Other languages
French (fr)
Japanese (ja)
Inventor
俊典 沖
貴幸 古田
Original Assignee
トヨタ自動車 株式会社
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 トヨタ自動車 株式会社 filed Critical トヨタ自動車 株式会社
Priority to PCT/JP2012/057734 priority Critical patent/WO2013145078A1/en
Publication of WO2013145078A1 publication Critical patent/WO2013145078A1/en

Links

Images

Classifications

    • 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
    • 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
    • F01D25/183—Sealing means
    • 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
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
    • F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
    • 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
    • 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
    • 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

Definitions

  • the present invention relates to an exhaust turbine supercharger mounted on an internal combustion engine.
  • FIG. 8 shows a cross-sectional structure of a conventional general exhaust turbine supercharger.
  • a thrust bearing 20 that receives the thrust force of the rotating shaft 2 of the compressor impeller 4 is provided inside the bearing housing 10.
  • the thrust bearing 20 includes a thrust collar 21 that rotates integrally with the rotary shaft 2, and a thrust disk 22 that is fitted in a groove 21 a formed on the outer peripheral surface of the thrust collar 21 and is fixed to the bearing housing 10. .
  • a seal ring collar 30 that rotates integrally with the rotary shaft 2 is provided between the thrust bearing 20 and the compressor impeller 4.
  • a seal retainer 40 is inserted into the bearing housing 10 from the outside of the thrust bearing 20.
  • the seal retainer 40 has a facing surface 41 that faces the outer peripheral surface of the seal ring collar 30, and a seal ring 39 is press-fitted into the facing surface 41.
  • the seal ring 39 is accommodated in a groove portion 31 formed on the outer peripheral surface of the seal ring collar 30.
  • the seal ring 39 and the groove portion 31 form a seal structure, and oil leakage to the compressor impeller 4 side is suppressed through the seal structure.
  • a substantially disc-shaped deflector 150 is provided in the recess 42 formed inside the seal retainer 40.
  • the rotating shaft 2 is inserted through the center hole 153 of the deflector 150.
  • the deflector 150 divides a space formed between the seal retainer 40 and the thrust bearing 20 into two chambers (first chamber C1 and second chamber C2). Further, a tongue piece 155 extends inward and downward from the vertical lower portion of the deflector 150.
  • oil is supplied to the groove portion 21a of the thrust collar 21 for lubrication through an oil passage formed inside the bearing housing 10.
  • the thrust collar 21 rotates integrally with the rotary shaft 2, the oil adhering to the thrust collar 21 scatters, and the scattered oil is collected by the deflector 150 and the tongue. It is discharged through the piece 155 to the drain passage. As a result, the inflow of oil into the second chamber C ⁇ b> 2 is suppressed, and oil leakage to the compressor impeller 4 side through the seal ring collar 30 and the seal retainer 40 is suppressed.
  • An object of the present invention is to reduce the amount of oil that stays in the second chamber, and to prevent the oil from leaking to the compressor impeller side through between the seal ring collar and the seal retainer opposed thereto. It is to provide a turbine supercharger.
  • the exhaust turbine supercharger rotationally drives the compressor impeller by the energy of the exhaust.
  • the exhaust turbine supercharger is positioned between the thrust bearing and the compressor impeller in the axial direction of the rotating shaft and is external to the rotating shaft in the axial direction of the rotating shaft.
  • a deflector that divides a space formed between the seal retainer and the thrust bearing into two chambers.
  • the flow direction of the air flow including the oil scattered by the centrifugal force generated with the rotation of the rotary shaft in the thrust bearing side chamber is defined as the air flow direction.
  • the deflector includes an introduction hole that penetrates the deflector, and a flange that extends from a first edge that is an upstream edge of the introduction hole in the airflow direction toward the thrust bearing.
  • the scissors are configured to be positioned closer to the thrust bearing toward the downstream side in the airflow direction, and the scissors together with the second edge that is the downstream edge in the airflow direction in the introduction hole. An opening that opens toward the downstream side is formed.
  • the chamber on the thrust bearing side is referred to as the first chamber and the chamber on the seal retainer side is referred to as the second chamber.
  • the soot of the above aspect is formed in the deflector, the flow cross-sectional area of the airflow including oil is reduced by the soot in the first chamber toward the downstream side in the airflow direction. .
  • the flow velocity increases and the pressure decreases.
  • a negative pressure is generated in the opening of the deflector in the first chamber.
  • the oil existing in the second chamber is sucked into the first chamber through the introduction hole and the opening due to the negative pressure generated in the first chamber. Accordingly, the amount of oil staying in the second chamber can be reduced, and oil can be prevented from leaking to the compressor impeller side between the seal ring collar and the seal retainer.
  • the first edge is an edge on the rear side in the rotation direction of the rotation shaft in the introduction hole
  • the second edge is an edge on the front side in the rotation direction of the rotation shaft in the introduction hole
  • the flange is positioned closer to the thrust bearing toward the front side in the rotation direction of the rotation shaft.
  • first edge is a radially inner edge of the introduction hole
  • second edge is a radially outer edge of the introduction hole
  • the flange is a radially outer edge of the introduction hole. A mode in which it is located closer to the thrust bearing is preferable.
  • a plurality of the introduction holes and the ridges are arranged in the circumferential direction of the deflector.
  • the introduction hole and the ridge are arranged above the lowest part in the vertical direction of the edge of the center hole.
  • the oil discharged from the second chamber or the first chamber to the drain passage may temporarily stay in the seal retainer. Further, the liquid level of the oil thus staying can reach the position immediately below the lowest part in the vertical direction of the edge of the central hole of the deflector. Therefore, even if the introduction hole and the ridge are arranged below the lowermost portion of the edge of the center hole in the vertical direction, the introduction hole and the ridge may not be able to generate the negative pressure as described above.
  • the arrangement positions of the introduction holes and the ridges can be accurately set, and unnecessary introduction holes and ridges need not be formed.
  • the deflector has a disc shape and an inner peripheral portion having the center hole, and an outer peripheral portion positioned closer to the seal retainer and radially outward than the inner peripheral portion. It is preferable that the ridge is formed on the inner periphery.
  • the arrangement positions of the introduction hole and the ridge are close to the rotation axis. For this reason, the airflow including oil reaches the soot before the flow velocity decreases, and an appropriate negative pressure can be generated at the opening. Therefore, the oil existing in the second chamber can be preferably sucked into the first chamber.
  • the introduction hole and the ridge are formed by pressing the deflector.
  • the deflector can be easily formed as compared with the aspect in which the member corresponding to the flange is formed on the main body by welding or the like. become.
  • Sectional drawing which shows the cross-sectional structure centering on a deflector about the exhaust turbine supercharger which concerns on one Embodiment of this invention.
  • Sectional drawing which shows the cross-section of the deflector in the embodiment.
  • the top view which shows the planar structure of the deflector seen from the arrow A direction of FIG.
  • FIG. 5 is a cross-sectional view showing a cross-sectional structure of the deflector along the line DD in FIG. 4.
  • the top view which shows the planar structure of the deflector corresponding to FIG. 4 about the modification of the embodiment.
  • the top view which shows the planar structure of the deflector corresponding to FIG. 4 about the other modification of the embodiment.
  • Sectional drawing which shows the cross-section of the conventional general exhaust turbine supercharger.
  • FIG. 1 shows a cross-sectional structure centered on a deflector for the exhaust turbine turbocharger of the present embodiment.
  • the upper part in the vertical direction is simply referred to as the upper part
  • the lower part in the vertical direction is simply referred to as the lower part.
  • the exhaust turbine supercharger includes a bearing housing 10 that surrounds a plurality of bearings that rotatably support the rotating shaft 2 of the compressor impeller 4.
  • a thrust bearing 20 that receives the thrust force of the rotating shaft 2 of the compressor impeller 4 is provided inside the bearing housing 10.
  • the thrust bearing 20 includes a thrust collar 21 that is externally fitted to the rotary shaft 2, and a thrust disk 22 that is fitted in a groove portion 21 a formed on the outer peripheral surface of the thrust collar 21.
  • the thrust collar 21 rotates integrally with the rotary shaft 2, while the thrust disk 22 is fixed to the bearing housing 10.
  • seal ring collar 30 that is externally fitted to the rotary shaft 2 and rotates integrally.
  • An annular groove 31 is formed on the outer peripheral surface of the seal ring collar 30.
  • An annular protrusion 32 is formed on the outer peripheral surface of the seal ring collar 30 closer to the thrust bearing 20 than the groove 31.
  • a seal retainer 40 is inserted into the bearing housing 10.
  • the seal retainer 40 is fixed to the bearing housing 10 with bolts.
  • the seal retainer 40 has a facing surface 41 that faces the outer peripheral surface of the seal ring collar 30, and a seal ring 39 is press-fitted into the facing surface 41.
  • the seal ring 39 is accommodated in the groove 31 of the seal ring collar 30.
  • the seal ring 39 and the groove portion 31 form a seal structure.
  • a substantially donut-shaped recess 42 is formed on the seal retainer 40 on the thrust bearing 20 side.
  • the end surface 43 of the seal retainer 40 on the thrust bearing 20 side (the end surface on the outer peripheral side of the recess 42) is in contact with the end surface of the thrust disk 22.
  • a substantially disc-shaped deflector 50 having a center hole 53 is provided in the recess 42 of the seal retainer 40, and the rotary shaft 2 is inserted through the center hole 53.
  • the central hole 53 of the deflector 50 is located closer to the thrust bearing 20 than the protrusion 32 of the seal ring collar 30.
  • the deflector 50 divides a space formed between the seal retainer 40 and the thrust bearing 20 into two chambers. Of the two chambers partitioned by the deflector 50, the chamber on the thrust bearing 20 side is referred to as a first chamber C1, and the chamber on the seal retainer 40 side is referred to as a second chamber C2.
  • oil is supplied for lubrication to the groove 21a of the thrust collar 21 through an oil passage formed inside the bearing housing 10.
  • FIG. 2 shows a cross-sectional structure of the deflector 50.
  • FIG. 3 shows a planar structure of the deflector 50 as viewed from the direction of arrow A in FIG.
  • FIG. 4 shows an enlarged view of part B of FIG.
  • FIG. 5 shows a cross-sectional structure of the deflector 50 along the line DD in FIG.
  • the deflector 50 is formed in a disc shape and has an inner peripheral portion 51 having the center hole 53, and is positioned on the seal retainer 40 side and radially outward from the inner peripheral portion 51.
  • the outer peripheral part 54 and the tongue piece 55 extended inclining from the lower part of the outer peripheral part 54 to the thrust bearing 20 side downward (lower right side in FIG. 2) are provided.
  • a plurality of penetrating the deflectors 50 are located above the lowermost part 52 a of the edge 52 of the center hole 53, that is, above the two-dot chain line L in FIGS. 2 and 3.
  • five) introduction holes 60 and flanges 70 are formed at equal intervals along the circumferential direction. The sizes of the introduction holes 60 and the flanges 70 and the distance between them and the center of the center hole 53 are the same.
  • the introduction hole 60 has an isosceles triangle shape. That is, the second edge 62 which is the edge of the introduction hole 60 on the front side in the rotation direction of the rotation shaft 2 extends along the radial direction Y and corresponds to the base of the isosceles triangle. Further, the first edge 61 that is the edge on the rear side in the rotation direction of the rotation shaft 2 in the introduction hole 60 corresponds to the vertex of the isosceles triangle.
  • ⁇ 70 extends from the first edge 61 toward the front side of the drawing, that is, toward the thrust bearing 20, and has a substantially triangular pyramid shape.
  • the surface including the second edge 62 in the triangular pyramid is an opening 80. That is, the flange 70 is positioned closer to the thrust bearing 20 toward the front side of the rotation shaft 2 in the rotation direction. Further, an opening 80 is formed by the second edge 62 and the flange 70.
  • the introduction hole 60 and the flange 70 are formed by pressing the deflector 50.
  • the deflector 50 is formed with the flange 70 of the above-described aspect, and therefore, in the first chamber C ⁇ b> 1, the front side in the rotation direction of the rotary shaft 2 by the same flange 70, The flow cross-sectional area of the air flow containing oil is reduced toward the downstream side in the air flow direction. For this reason, when the airflow containing oil passes the eaves 70, the flow velocity increases and the pressure decreases. Thereby, a negative pressure is generated in the opening 80 of the deflector 50 in the first chamber C1. As a result, as indicated by an arrow N in FIG.
  • the oil present in the second chamber C2 is sucked into the first chamber C1 through the introduction hole 60 due to the negative pressure generated in the first chamber C1.
  • the number of introduction holes 60 and the ridges 70, their arrangement positions, and their sizes are set through experiments and simulations so as to generate an appropriate magnitude of negative pressure in the opening 80.
  • the flange 70 is provided so that the opening 80 opens toward the front side in the rotation direction of the rotary shaft 2, that is, toward the downstream side in the airflow direction, the oil scattered by the centrifugal force is directly passed through the introduction hole 60. Outflow to the second chamber C2 is suppressed.
  • the oil discharged from the second chamber C2 or the first chamber C1 to the drain passage may temporarily stay in the recess 42 of the seal retainer 40.
  • the level of the oil remaining in this way can reach the position immediately below the lowermost part 52a in the edge 52 of the center hole 53 of the deflector 50, as shown by a one-dot chain line in FIG. Therefore, even if the introduction hole and the ridge are formed below the lowermost portion 52a in the vertical direction of the edge 52 of the center hole 53, the introduction hole and the ridge may not be able to generate the negative pressure as described above. There is.
  • the arrangement positions of the introduction hole 60 and the flange 70 can be accurately set, and unnecessary introduction holes and flanges need not be formed.
  • the arrangement positions of the introduction hole 60 and the flange 70 are close to the rotary shaft 2. It becomes. For this reason, before the flow velocity decreases, the airflow including oil reaches the ridge 70, and an appropriate amount of negative pressure can be generated in the opening 80. Therefore, the oil present in the second chamber C2 can be preferably sucked into the first chamber C1.
  • the deflector 50 of the exhaust turbine supercharger includes an introduction hole 60 penetrating the deflector 50 and an edge (first edge) 61 on the rear side in the rotation direction of the rotary shaft 2 in the introduction hole 60 from a thrust bearing. And a ridge 70 extending toward 20.
  • the flange 70 is located closer to the thrust bearing 20 toward the front side in the rotational direction of the rotary shaft 2.
  • an opening 80 is formed by the edge (second edge) 62 and the flange 70 on the front side in the rotation direction of the rotation shaft 2 in the introduction hole 60.
  • a plurality of introduction holes 60 and ridges 70 are arranged in the circumferential direction of the deflector 50. According to such a configuration, a negative pressure is generated in each of the openings 80 arranged at a plurality of positions in the circumferential direction of the deflector 50. As a result, oil present at different positions in the second chamber C2 is sucked into the first chamber C1 through the respective introduction holes 60. Therefore, the amount of oil staying in the second chamber C2 can be accurately reduced.
  • the introduction hole 60 and the flange 70 are disposed above the lowermost part 52 a in the vertical direction of the edge 52 of the center hole 53. According to such a configuration, the arrangement positions of the introduction hole 60 and the collar 70 can be set accurately, and unnecessary introduction holes and collars need not be formed.
  • the deflector 50 has a disc shape and has an inner peripheral portion 51 having a center hole 53, and is positioned closer to the seal retainer 40 and radially outward than the inner peripheral portion 51, and contacts the inner wall of the seal retainer 40. And an outer peripheral portion 54 in contact therewith.
  • the introduction hole 60 and the flange 70 are formed in the inner peripheral portion 51. According to such a configuration, an air stream containing oil can reach the ridge 70 before the flow velocity decreases, and a negative pressure of an appropriate magnitude can be generated in the opening 80. Therefore, the oil present in the second chamber C2 can be preferably sucked into the first chamber C1.
  • the introduction hole 60 and the flange 70 are formed by pressing the deflector 50. According to such a configuration, for example, after the introduction hole is formed in the main body of the deflector, the deflector 50 can be easily formed as compared with an aspect in which a member corresponding to the flange is formed on the main body by welding or the like. It becomes like this.
  • exhaust turbine supercharger is not limited to the configuration exemplified in the above-described embodiment, and may be implemented as, for example, the following form appropriately modified.
  • the shapes of the introduction hole 60, the flange 70, and the opening 80 are not limited to those illustrated in the above embodiment.
  • the introduction hole 260 may have a substantially cup shape
  • the flange 270 may have a curved surface shape
  • the opening 280 may have a substantially semi-elliptical shape. Also in this case, it is desirable to form the introduction hole 260 and the flange 270 by press working.
  • the introduction hole and the ridge 70 are formed by pressing, but the formation mode of the ridge according to the present invention is not limited to this.
  • a member corresponding to the flange may be formed on the main body by welding or the like.
  • the outer peripheral portion 54 of the deflector 50 is positioned closer to the seal retainer 40 than the inner peripheral portion 51.
  • the outer peripheral portion of the deflector is positioned closer to the thrust bearing 20 than the inner peripheral portion. It can also be adopted. Even in this case, it is desirable to form the introduction hole and the flange in the inner peripheral portion in the same manner as in the above-described embodiment in order to generate a negative pressure of an appropriate magnitude in the opening.
  • introduction holes and ridges are not limited to those illustrated in the above embodiment, but experiments such that an appropriate negative pressure is generated at the opening, etc. Can be changed as appropriate.
  • a plurality of introduction holes and ridges may be provided in the radial direction.
  • the introduction hole 60 and the flange 70 are arranged at a position where the airflow direction is along the rotation direction of the rotary shaft 2.
  • the airflow direction gradually follows the radial direction from the rotation direction of the rotation shaft 2 as the introduction position of the introduction hole and the flange approaches the axis of the rotation shaft 2. Therefore, for example, when the introduction hole and the ridge are arranged at a position where the airflow direction is along the radial direction of the rotary shaft 2, the introduction hole 360 and the ridge 370 are formed in the deflector 350 as shown in FIG. Is desirable. That is, as shown in FIG.
  • the flange 370 extends from the radially inner edge 361 of the introduction hole 360 toward the front side of the sheet, that is, toward the thrust bearing 20 and toward the radially outer side of the introduction hole 360 toward the thrust bearing 20. It is located near.
  • the opening 380 is formed by a radially outer edge 362 and a flange 370 in the introduction hole 360.
  • Tongue piece 60, 260, 360 ... Introduction hole, 61 ... Edge on the rear side in the rotational direction, 62 ... Edge on the front side in the rotational direction, 70, 270 ... ⁇ , 80, 280, 380... Opening, 361... Radially inner edge, 362.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Supercharger (AREA)

Abstract

A deflector (50) for an exhaust turbine supercharger is provided with an introduction hole (60) penetrating through the deflector (50) and with eaves (70) extending toward a thrust bearing (20) from the edge (61) of the introduction hole (60) which is located behind in the rotational direction of a rotating shaft (2). The eaves (70) are provided so as to more closely approach the thrust bearing (20) as the eaves (70) extend ahead in the rotational direction of the rotating shaft (2). Also, an opening (80) is formed by the eaves (70) and the edge (62) of the introduction hole (60) which is located ahead in the rotational direction of the rotating shaft (2).

Description

排気タービン過給機Exhaust turbine turbocharger
　本発明は、内燃機関に搭載される排気タービン過給機に関する。 The present invention relates to an exhaust turbine supercharger mounted on an internal combustion engine.
　従来、排気のエネルギによってコンプレッサインペラを回転駆動する排気タービン過給機が周知である（例えば特許文献１参照）。図８に従来一般の排気タービン過給機の断面構造を示す。 Conventionally, an exhaust turbine supercharger that rotationally drives a compressor impeller by exhaust energy is well known (see, for example, Patent Document 1). FIG. 8 shows a cross-sectional structure of a conventional general exhaust turbine supercharger.
　図８に示すように、ベアリングハウジング１０の内部には、コンプレッサインペラ４の回転軸２のスラスト力を受けるスラストベアリング２０が設けられている。スラストベアリング２０は、回転軸２と一体回転するスラストカラー２１と、同スラストカラー２１の外周面に形成された溝部２１ａに嵌められるとともにベアリングハウジング１０に固定されたスラストディスク２２とから構成されている。 As shown in FIG. 8, a thrust bearing 20 that receives the thrust force of the rotating shaft 2 of the compressor impeller 4 is provided inside the bearing housing 10. The thrust bearing 20 includes a thrust collar 21 that rotates integrally with the rotary shaft 2, and a thrust disk 22 that is fitted in a groove 21 a formed on the outer peripheral surface of the thrust collar 21 and is fixed to the bearing housing 10. .
　スラストベアリング２０とコンプレッサインペラ４との間には、回転軸２と一体回転するシールリングカラー３０が設けられている。 A seal ring collar 30 that rotates integrally with the rotary shaft 2 is provided between the thrust bearing 20 and the compressor impeller 4.
　ベアリングハウジング１０の内部にはスラストベアリング２０の外側からシールリテーナ４０が嵌挿されている。シールリテーナ４０は、シールリングカラー３０の外周面に対向する対向面４１を有しており、同対向面４１にはシールリング３９が圧入されている。シールリング３９はシールリングカラー３０の外周面に形成された溝部３１内に収容されている。そして、これらシールリング３９と溝部３１とによってシール構造が形成されており、同シール構造を通じてコンプレッサインペラ４側へのオイルの漏出が抑制されるようになっている。 A seal retainer 40 is inserted into the bearing housing 10 from the outside of the thrust bearing 20. The seal retainer 40 has a facing surface 41 that faces the outer peripheral surface of the seal ring collar 30, and a seal ring 39 is press-fitted into the facing surface 41. The seal ring 39 is accommodated in a groove portion 31 formed on the outer peripheral surface of the seal ring collar 30. The seal ring 39 and the groove portion 31 form a seal structure, and oil leakage to the compressor impeller 4 side is suppressed through the seal structure.
　シールリテーナ４０の内側に形成された凹部４２には略円板状のデフレクタ１５０が設けられている。デフレクタ１５０の中心孔１５３には回転軸２が挿通されている。このデフレクタ１５０によって、シールリテーナ４０とスラストベアリング２０との間に形成される空間が２つの室（第１室Ｃ１、第２室Ｃ２）に区画されている。また、デフレクタ１５０の鉛直方向下部から舌片１５５が内側下方に延びている。 A substantially disc-shaped deflector 150 is provided in the recess 42 formed inside the seal retainer 40. The rotating shaft 2 is inserted through the center hole 153 of the deflector 150. The deflector 150 divides a space formed between the seal retainer 40 and the thrust bearing 20 into two chambers (first chamber C1 and second chamber C2). Further, a tongue piece 155 extends inward and downward from the vertical lower portion of the deflector 150.
　こうした排気タービン過給機では、ベアリングハウジング１０の内部に形成された油路を通じてスラストカラー２１の溝部２１ａ等に対して潤滑のためにオイルが供給されるようになっている。 In such an exhaust turbine supercharger, oil is supplied to the groove portion 21a of the thrust collar 21 for lubrication through an oil passage formed inside the bearing housing 10.
　ここで、スラストカラー２１は回転軸２と一体に回転することから、同スラストカラー２１に付着しているオイルが飛散することになるが、こうして飛散したオイルはデフレクタ１５０によって捕集されるとともに舌片１５５を伝ってドレイン通路へと排出される。これにより、第２室Ｃ２内へのオイルの流入が抑制され、シールリングカラー３０とシールリテーナ４０との間を通じてコンプレッサインペラ４側にオイルが漏出することが抑制される。 Here, since the thrust collar 21 rotates integrally with the rotary shaft 2, the oil adhering to the thrust collar 21 scatters, and the scattered oil is collected by the deflector 150 and the tongue. It is discharged through the piece 155 to the drain passage. As a result, the inflow of oil into the second chamber C <b> 2 is suppressed, and oil leakage to the compressor impeller 4 side through the seal ring collar 30 and the seal retainer 40 is suppressed.
特開平９―２６４１５１号公報JP-A-9-264151
　ところで、こうした従来の排気タービン過給機では、内燃機関の吸気通路内が負圧となると、第１室Ｃ１内に存在するオイルがデフレクタ１５０の中心孔１５３を通じて第２室Ｃ２に吸引され、更に、シールリングカラー３０とシールリテーナ４０との間を通じてコンプレッサインペラ４側に漏出するおそれがある。その結果、オイル消費量が増大するといった問題が生じることとなる。 By the way, in such a conventional exhaust turbine supercharger, when the pressure in the intake passage of the internal combustion engine becomes negative, oil existing in the first chamber C1 is sucked into the second chamber C2 through the center hole 153 of the deflector 150, and further There is a risk of leakage to the compressor impeller 4 side through between the seal ring collar 30 and the seal retainer 40. As a result, there arises a problem that the oil consumption increases.
　本発明の目的は、第２室内に滞留するオイルの量を低減して、シールリングカラーとこれに対向するシールリテーナとの間を通じてコンプレッサインペラ側にオイルが漏出することを抑制することのできる排気タービン過給機を提供することにある。 An object of the present invention is to reduce the amount of oil that stays in the second chamber, and to prevent the oil from leaking to the compressor impeller side through between the seal ring collar and the seal retainer opposed thereto. It is to provide a turbine supercharger.
　上記目的を達成するため、本発明に従う排気タービン過給機は、排気のエネルギによってコンプレッサインペラを回転駆動する。また、排気タービン過給機は、前記コンプレッサインペラの回転軸のスラスト力を受けるスラストベアリングと、前記回転軸の軸線方向において前記スラストベアリングと前記コンプレッサインペラとの間に位置するとともに前記回転軸に外嵌されるシールリングカラーと、前記シールリングカラーの外周面に対向する対向面を有するとともに同対向面にてシールリングを保持するシールリテーナと、略円板状をなすとともに前記回転軸が挿通される中心孔を有するデフレクタであって前記シールリテーナと前記スラストベアリングとの間に形成される空間を２つの室に区画するデフレクタと、を備える。前記２つの室のうち前記スラストベアリング側の室内において前記回転軸の回転に伴い発生する遠心力により飛散したオイルを含む気流の流れ方向を気流流れ方向と定義する。前記デフレクタは、同デフレクタを貫通する導入孔と、同導入孔における前記気流流れ方向の上流側の縁部である第１縁部から前記スラストベアリングに向かって延びる庇と、を有する。前記庇は前記気流流れ方向の下流側ほど前記スラストベアリング寄りに位置するように構成されるとともに、同庇は前記導入孔における前記気流流れ方向の下流側の縁部である第２縁部と共に当該下流側に向けて開口する開口部を形成する。 In order to achieve the above object, the exhaust turbine supercharger according to the present invention rotationally drives the compressor impeller by the energy of the exhaust. The exhaust turbine supercharger is positioned between the thrust bearing and the compressor impeller in the axial direction of the rotating shaft and is external to the rotating shaft in the axial direction of the rotating shaft. A seal ring collar to be fitted, a seal retainer having a facing surface facing the outer peripheral surface of the seal ring collar and holding the seal ring on the facing surface, and having a substantially disc shape and the rotating shaft being inserted therethrough And a deflector that divides a space formed between the seal retainer and the thrust bearing into two chambers. Of the two chambers, the flow direction of the air flow including the oil scattered by the centrifugal force generated with the rotation of the rotary shaft in the thrust bearing side chamber is defined as the air flow direction. The deflector includes an introduction hole that penetrates the deflector, and a flange that extends from a first edge that is an upstream edge of the introduction hole in the airflow direction toward the thrust bearing. The scissors are configured to be positioned closer to the thrust bearing toward the downstream side in the airflow direction, and the scissors together with the second edge that is the downstream edge in the airflow direction in the introduction hole. An opening that opens toward the downstream side is formed.
　以降において、デフレクタにより区画される２つの室のうちスラストベアリング側の室を第１室と称するとともにシールリテーナ側の室を第２室と称することとする。 Hereinafter, of the two chambers partitioned by the deflector, the chamber on the thrust bearing side is referred to as the first chamber and the chamber on the seal retainer side is referred to as the second chamber.
　第１室内では、回転軸の回転に伴い発生する遠心力によってオイルが飛散するとともに空気の流れが生じる。ここで、上記態様によれば、デフレクタには上記態様の庇が形成されているため、第１室内においては上記庇によって気流流れ方向の下流側ほどオイルを含む気流の流通断面積が小さくされる。このため、オイルを含む気流が庇を通過する際にその流速が上昇するとともにその圧力が低下するようになる。これにより、第１室内においてデフレクタの開口部では負圧が発生するようになる。その結果、第１室内において発生する負圧によって第２室内に存在するオイルが導入孔及び開口部を通じて第１室に吸引されるようになる。従って、第２室内に滞留するオイルの量を低減することができ、シールリングカラーとシールリテーナとの間を通じてコンプレッサインペラ側にオイルが漏出することを抑制することができるようになる。 In the first chamber, oil is scattered and air flows due to the centrifugal force generated by the rotation of the rotating shaft. Here, according to the above aspect, since the soot of the above aspect is formed in the deflector, the flow cross-sectional area of the airflow including oil is reduced by the soot in the first chamber toward the downstream side in the airflow direction. . For this reason, when the airflow containing oil passes the soot, the flow velocity increases and the pressure decreases. Thereby, a negative pressure is generated in the opening of the deflector in the first chamber. As a result, the oil existing in the second chamber is sucked into the first chamber through the introduction hole and the opening due to the negative pressure generated in the first chamber. Accordingly, the amount of oil staying in the second chamber can be reduced, and oil can be prevented from leaking to the compressor impeller side between the seal ring collar and the seal retainer.
　この場合、前記第１縁部は前記導入孔における前記回転軸の回転方向後側の縁部であり、前記第２縁部は前記導入孔における前記回転軸の回転方向前側の縁部であり、前記庇は前記回転軸の回転方向前側ほど前記スラストベアリング寄りに位置するといった態様が好ましい。 In this case, the first edge is an edge on the rear side in the rotation direction of the rotation shaft in the introduction hole, and the second edge is an edge on the front side in the rotation direction of the rotation shaft in the introduction hole, It is preferable that the flange is positioned closer to the thrust bearing toward the front side in the rotation direction of the rotation shaft.
　導入孔及び庇の配置位置が回転軸の軸心から離間するほど気流流れ方向は回転軸の回転方向に沿うようになる。このため、デフレクタにおいて気流流れ方向が回転軸の回転方向に沿うような位置に導入孔及び庇が配置される構成に対して上記態様を適用すれば、庇及び開口部の構造を適切なものとすることができる。 ¡The air flow direction becomes along the rotation direction of the rotary shaft as the arrangement position of the introduction hole and the soot is separated from the axis of the rotary shaft. For this reason, if the said aspect is applied with respect to the structure by which an introduction hole and a cage | basket are arrange | positioned in a position where an airflow flow direction follows the rotation direction of a rotating shaft in a deflector, the structure of a cage | basket and an opening part will be appropriate. can do.
　また、前記第１縁部は前記導入孔における径方向内側の縁部であり、前記第２縁部は前記導入孔における径方向外側の縁部であり、前記庇は前記導入孔における径方向外側ほど前記スラストベアリング寄りに位置するといった態様が好ましい。 Further, the first edge is a radially inner edge of the introduction hole, the second edge is a radially outer edge of the introduction hole, and the flange is a radially outer edge of the introduction hole. A mode in which it is located closer to the thrust bearing is preferable.
　導入孔及び庇の配置位置が回転軸の軸心に近接するほど気流流れ方向は径方向に沿うようになる。このため、デフレクタにおいて気流流れ方向が径方向に沿うような位置に導入孔及び庇が配置される構成に対して上記態様を適用すれば、庇及び開口部の構造を適切なものとすることができる。 ¡The closer the position of the introduction hole and the soot is to the axis of the rotating shaft, the more the airflow direction is along the radial direction. For this reason, if the said aspect is applied with respect to the structure by which an introduction hole and a wrinkle are arrange | positioned in a position where an airflow direction is along a radial direction in a deflector, the structure of a wrinkle and an opening part may be made appropriate. it can.
　また、前記導入孔及び前記庇は前記デフレクタの周方向において複数配置されているといった態様が好ましい。 Further, it is preferable that a plurality of the introduction holes and the ridges are arranged in the circumferential direction of the deflector.
　同態様によれば、デフレクタの周方向における複数の位置に形成された開口部においてそれぞれ負圧が発生するようになる。これにより、第２室内において異なる位置に存在するオイルが各導入孔を通じて第１室に吸引されるようになる。従って、第２室内に滞留するオイルの量を的確に低減することができるようになる。尚、導入孔及び庇の個数、それらの配置位置、及びそれらの大きさは、実験やシミュレーションを通じて設定することが望ましい。 According to the same mode, negative pressure is generated in the openings formed at a plurality of positions in the circumferential direction of the deflector. As a result, oil present at different positions in the second chamber is sucked into the first chamber through the introduction holes. Therefore, the amount of oil that stays in the second chamber can be accurately reduced. In addition, it is desirable to set the number of introduction holes and ridges, their arrangement positions, and their sizes through experiments and simulations.
　また、前記導入孔及び前記庇は前記中心孔の縁部の鉛直方向における最下部よりも上側に配置されているといった態様が好ましい。 Further, it is preferable that the introduction hole and the ridge are arranged above the lowest part in the vertical direction of the edge of the center hole.
　第２室や第１室からドレイン通路へ排出されるオイルがシールリテーナ内において一時的に滞留することがある。またこうして滞留するオイルの液面は、デフレクタの中心孔の縁部の鉛直方向における最下部の直下まで到達し得る。そのため、導入孔及び庇を中心孔の縁部の鉛直方向における最下部よりも下側に配置したとしても、それら導入孔及び庇では前述したような負圧を発生させることができないおそれがある。 The oil discharged from the second chamber or the first chamber to the drain passage may temporarily stay in the seal retainer. Further, the liquid level of the oil thus staying can reach the position immediately below the lowest part in the vertical direction of the edge of the central hole of the deflector. Therefore, even if the introduction hole and the ridge are arranged below the lowermost portion of the edge of the center hole in the vertical direction, the introduction hole and the ridge may not be able to generate the negative pressure as described above.
　この点、上記態様によれば、導入孔及び庇の配置位置を的確に設定することができ、不要な導入孔及び庇を形成しなくとも済む。 In this respect, according to the above aspect, the arrangement positions of the introduction holes and the ridges can be accurately set, and unnecessary introduction holes and ridges need not be formed.
　また、前記デフレクタは円板状をなすとともに前記中心孔を有する内周部と、同内周部よりも前記シールリテーナ寄りで且つ径方向外側に位置する外周部とを有し、前記導入孔及び前記庇は前記内周部に形成されているといった態様が好ましい。 The deflector has a disc shape and an inner peripheral portion having the center hole, and an outer peripheral portion positioned closer to the seal retainer and radially outward than the inner peripheral portion. It is preferable that the ridge is formed on the inner periphery.
　導入孔及び庇の配置位置が回転軸から離間するほど、庇に到達するまでにオイルを含む気流の流速が低下してしまい、開口部において発生する負圧が小さくなり、第２室内に存在するオイルを第１室に好適に吸引することができないおそれがある。 The farther the arrangement position of the introduction hole and the soot is from the rotary shaft, the lower the flow rate of the airflow including oil before reaching the soot, and the negative pressure generated in the opening becomes smaller and exists in the second chamber. There is a possibility that the oil cannot be suitably sucked into the first chamber.
　この点、上記態様によれば、導入孔及び庇がデフレクタの内周部に形成されているため、導入孔及び庇の配置位置が回転軸に対して近接したものとなる。このため、流速が低下する前にオイルを含む気流が庇に到達するようになり、開口部において適切な大きさの負圧を発生させることができるようになる。従って、第２室内に存在するオイルを第１室に吸引することが好適にできるようになる。 In this respect, according to the above aspect, since the introduction hole and the ridge are formed in the inner peripheral portion of the deflector, the arrangement positions of the introduction hole and the ridge are close to the rotation axis. For this reason, the airflow including oil reaches the soot before the flow velocity decreases, and an appropriate negative pressure can be generated at the opening. Therefore, the oil existing in the second chamber can be preferably sucked into the first chamber.
　また、前記導入孔及び前記庇は前記デフレクタをプレス加工することにより形成されているといった態様が好ましい。 Further, it is preferable that the introduction hole and the ridge are formed by pressing the deflector.
　同態様によれば、例えばデフレクタの本体に導入孔を形成した後、この本体に対して庇に対応する部材を溶着等にて形成する態様に比べて、デフレクタを容易に形成することができるようになる。 According to this aspect, for example, after the introduction hole is formed in the main body of the deflector, the deflector can be easily formed as compared with the aspect in which the member corresponding to the flange is formed on the main body by welding or the like. become.
本発明の一実施形態に係る排気タービン過給機について、デフレクタを中心とした断面構造を示す断面図。BRIEF DESCRIPTION OF THE DRAWINGS Sectional drawing which shows the cross-sectional structure centering on a deflector about the exhaust turbine supercharger which concerns on one Embodiment of this invention. 同実施形態におけるデフレクタの断面構造を示す断面図。Sectional drawing which shows the cross-section of the deflector in the embodiment. 図２の矢印Ａ方向から視たデフレクタの平面構造を示す平面図。The top view which shows the planar structure of the deflector seen from the arrow A direction of FIG. 図３のＢ部を拡大して示す拡大図。The enlarged view which expands and shows the B section of FIG. 図４のＤ－Ｄ線に沿ったデフレクタの断面構造を示す断面図。FIG. 5 is a cross-sectional view showing a cross-sectional structure of the deflector along the line DD in FIG. 4. 同実施形態の変形例について、図４に対応するデフレクタの平面構造を示す平面図。The top view which shows the planar structure of the deflector corresponding to FIG. 4 about the modification of the embodiment. 同実施形態の他の変形例について、図４に対応するデフレクタの平面構造を示す平面図。The top view which shows the planar structure of the deflector corresponding to FIG. 4 about the other modification of the embodiment. 従来一般の排気タービン過給機の断面構造を示す断面図。Sectional drawing which shows the cross-section of the conventional general exhaust turbine supercharger.
　以下、図１～図５を参照して、本発明を具体化した一実施形態について説明する。 Hereinafter, an embodiment embodying the present invention will be described with reference to FIGS.
　図１に、本実施形態の排気タービン過給機について、デフレクタを中心とした断面構造を示す。尚、以降において、鉛直方向上方を単に上方と称し、鉛直方向下方を単に下方と称することとする。 FIG. 1 shows a cross-sectional structure centered on a deflector for the exhaust turbine turbocharger of the present embodiment. In the following, the upper part in the vertical direction is simply referred to as the upper part, and the lower part in the vertical direction is simply referred to as the lower part.
　図１に示すように、排気タービン過給機は、コンプレッサインペラ４の回転軸２を回転自在に支持する複数のベアリングを囲繞するベアリングハウジング１０を備えている。 As shown in FIG. 1, the exhaust turbine supercharger includes a bearing housing 10 that surrounds a plurality of bearings that rotatably support the rotating shaft 2 of the compressor impeller 4.
　具体的には、ベアリングハウジング１０の内部には、コンプレッサインペラ４の回転軸２のスラスト力を受けるスラストベアリング２０が設けられている。スラストベアリング２０は、回転軸２に外嵌されたスラストカラー２１と、同スラストカラー２１の外周面に形成された溝部２１ａに嵌められたスラストディスク２２とから構成されている。スラストカラー２１は回転軸２と一体回転する一方、スラストディスク２２はベアリングハウジング１０に対して固定されている。 Specifically, a thrust bearing 20 that receives the thrust force of the rotating shaft 2 of the compressor impeller 4 is provided inside the bearing housing 10. The thrust bearing 20 includes a thrust collar 21 that is externally fitted to the rotary shaft 2, and a thrust disk 22 that is fitted in a groove portion 21 a formed on the outer peripheral surface of the thrust collar 21. The thrust collar 21 rotates integrally with the rotary shaft 2, while the thrust disk 22 is fixed to the bearing housing 10.
　スラストベアリング２０とコンプレッサインペラ４との間には、回転軸２に外嵌されて一体回転するシールリングカラー３０が設けられている。シールリングカラー３０の外周面には環状の溝部３１が形成されている。またシールリングカラー３０の外周面には、溝部３１よりもスラストベアリング２０側に環状の突部３２が形成されている。 Between the thrust bearing 20 and the compressor impeller 4, there is provided a seal ring collar 30 that is externally fitted to the rotary shaft 2 and rotates integrally. An annular groove 31 is formed on the outer peripheral surface of the seal ring collar 30. An annular protrusion 32 is formed on the outer peripheral surface of the seal ring collar 30 closer to the thrust bearing 20 than the groove 31.
　またベアリングハウジング１０の内部には、シールリテーナ４０が嵌挿されている。シールリテーナ４０はボルトによってベアリングハウジング１０に固定されている。シールリテーナ４０は、シールリングカラー３０の外周面に対向する対向面４１を有しており、同対向面４１にはシールリング３９が圧入されている。ちなみに、シールリング３９はシールリングカラー３０の上記溝部３１内に収容されている。そして、これらシールリング３９と溝部３１とによってシール構造が形成されている。シールリテーナ４０のスラストベアリング２０側には略ドーナツ状の凹部４２が形成されている。シールリテーナ４０のスラストベアリング２０側の端面４３（凹部４２の外周側の端面）はスラストディスク２２の端面に接している。 Further, a seal retainer 40 is inserted into the bearing housing 10. The seal retainer 40 is fixed to the bearing housing 10 with bolts. The seal retainer 40 has a facing surface 41 that faces the outer peripheral surface of the seal ring collar 30, and a seal ring 39 is press-fitted into the facing surface 41. Incidentally, the seal ring 39 is accommodated in the groove 31 of the seal ring collar 30. The seal ring 39 and the groove portion 31 form a seal structure. A substantially donut-shaped recess 42 is formed on the seal retainer 40 on the thrust bearing 20 side. The end surface 43 of the seal retainer 40 on the thrust bearing 20 side (the end surface on the outer peripheral side of the recess 42) is in contact with the end surface of the thrust disk 22.
　シールリテーナ４０の凹部４２には中心孔５３を有する略円板状のデフレクタ５０が設けられており、同中心孔５３には回転軸２が挿通されている。デフレクタ５０の中心孔５３はシールリングカラー３０の突部３２よりもスラストベアリング２０側に位置している。このデフレクタ５０によって、シールリテーナ４０とスラストベアリング２０との間に形成される空間が２つの室に区画される。尚、デフレクタ５０により区画される２つの室のうちスラストベアリング２０側の室を第１室Ｃ１と称するとともにシールリテーナ４０側の室を第２室Ｃ２と称することとする。 A substantially disc-shaped deflector 50 having a center hole 53 is provided in the recess 42 of the seal retainer 40, and the rotary shaft 2 is inserted through the center hole 53. The central hole 53 of the deflector 50 is located closer to the thrust bearing 20 than the protrusion 32 of the seal ring collar 30. The deflector 50 divides a space formed between the seal retainer 40 and the thrust bearing 20 into two chambers. Of the two chambers partitioned by the deflector 50, the chamber on the thrust bearing 20 side is referred to as a first chamber C1, and the chamber on the seal retainer 40 side is referred to as a second chamber C2.
　また、ベアリングハウジング１０の内部に形成された油路を通じてスラストカラー２１の溝部２１ａ等に対して潤滑のためにオイルが供給されるようになっている。 Further, oil is supplied for lubrication to the groove 21a of the thrust collar 21 through an oil passage formed inside the bearing housing 10.
　ここで、図２～図５を参照して、デフレクタ５０の構造について詳細に説明する。 Here, the structure of the deflector 50 will be described in detail with reference to FIGS.
　図２に、デフレクタ５０の断面構造を示す。図３に、図２の矢印Ａ方向から視たデフレクタ５０の平面構造を示す。図４に、図３のＢ部を拡大して示す。また、図５に、図４のＤ－Ｄ線に沿ったデフレクタ５０の断面構造を示す。 FIG. 2 shows a cross-sectional structure of the deflector 50. FIG. 3 shows a planar structure of the deflector 50 as viewed from the direction of arrow A in FIG. FIG. 4 shows an enlarged view of part B of FIG. FIG. 5 shows a cross-sectional structure of the deflector 50 along the line DD in FIG.
　図２及び図３に示すように、デフレクタ５０は、円板状をなすとともに上記中心孔５３を有する内周部５１と、同内周部５１よりもシールリテーナ４０側且つ径方向外側に位置する外周部５４と、同外周部５４の下部からスラストベアリング２０側下方（図２において右側下方）に傾斜して延びる舌片５５とを備えている。尚、図３に矢印Ｒで示す方向は回転軸２の回転方向である。 As shown in FIGS. 2 and 3, the deflector 50 is formed in a disc shape and has an inner peripheral portion 51 having the center hole 53, and is positioned on the seal retainer 40 side and radially outward from the inner peripheral portion 51. The outer peripheral part 54 and the tongue piece 55 extended inclining from the lower part of the outer peripheral part 54 to the thrust bearing 20 side downward (lower right side in FIG. 2) are provided. In addition, the direction shown by the arrow R in FIG.
　ここで、内周部５１において中心孔５３の縁部５２の最下部５２ａよりも上側、すなわち図２及び図３における二点鎖線Ｌよりも上側には、デフレクタ５０を貫通する複数（本実施形態では５つ）の導入孔６０及び庇７０が周方向に沿って等間隔にて形成されている。各導入孔６０及び庇７０の大きさ及びこれらと中心孔５３の中心との距離は同一とされている。 Here, in the inner peripheral portion 51, a plurality of penetrating the deflectors 50 (this embodiment) are located above the lowermost part 52 a of the edge 52 of the center hole 53, that is, above the two-dot chain line L in FIGS. 2 and 3. Then, five) introduction holes 60 and flanges 70 are formed at equal intervals along the circumferential direction. The sizes of the introduction holes 60 and the flanges 70 and the distance between them and the center of the center hole 53 are the same.
　詳しくは、図４に示すように、導入孔６０は、二等辺三角形状をなしている。すなわち、導入孔６０における回転軸２の回転方向前側の縁部である第２縁部６２は径方向Ｙに沿って延びるとともに当該二等辺三角形の底辺に対応している。また、導入孔６０における回転軸２の回転方向後側の縁部である第１縁部６１が当該二等辺三角形の頂点に対応している。 Specifically, as shown in FIG. 4, the introduction hole 60 has an isosceles triangle shape. That is, the second edge 62 which is the edge of the introduction hole 60 on the front side in the rotation direction of the rotation shaft 2 extends along the radial direction Y and corresponds to the base of the isosceles triangle. Further, the first edge 61 that is the edge on the rear side in the rotation direction of the rotation shaft 2 in the introduction hole 60 corresponds to the vertex of the isosceles triangle.
　庇７０は、第１縁部６１から図面手前側、すなわちスラストベアリング２０に向かって延びており、略三角錐形状をなしている。ただし、この三角錐において上記第２縁部６２を含む面は開口部８０とされている。すなわち、庇７０は回転軸２の回転方向前側ほどスラストベアリング２０寄りに位置している。また、第２縁部６２と庇７０とにより開口部８０が形成されている。ちなみに、導入孔６０及び庇７０はデフレクタ５０をプレス加工することにより形成されている。 庇 70 extends from the first edge 61 toward the front side of the drawing, that is, toward the thrust bearing 20, and has a substantially triangular pyramid shape. However, the surface including the second edge 62 in the triangular pyramid is an opening 80. That is, the flange 70 is positioned closer to the thrust bearing 20 toward the front side of the rotation shaft 2 in the rotation direction. Further, an opening 80 is formed by the second edge 62 and the flange 70. Incidentally, the introduction hole 60 and the flange 70 are formed by pressing the deflector 50.
　次に、本実施形態の作用について説明する。 Next, the operation of this embodiment will be described.
　図３に矢印Ｆにて示すように、第１室Ｃ１内では、回転軸２の回転に伴い発生する遠心力によってオイルが飛散するとともに空気の流れが生じる。そして、飛散したオイルを含む気流は導入孔６０及び庇７０の配置位置においては回転軸２の回転方向Ｒに沿って流れるようになる。 As shown by an arrow F in FIG. 3, in the first chamber C <b> 1, oil is scattered and air flows due to the centrifugal force generated with the rotation of the rotating shaft 2. The airflow including the scattered oil flows along the rotation direction R of the rotary shaft 2 at the position where the introduction hole 60 and the flange 70 are disposed.
　ここで、図４及び図５に示すように、デフレクタ５０には上記態様の庇７０が形成されているため、第１室Ｃ１内においては同庇７０によって回転軸２の回転方向前側ほど、すなわち気流流れ方向の下流側ほどオイルを含む気流の流通断面積が小さくされる。このため、オイルを含む気流が庇７０を通過する際にその流速が上昇するとともにその圧力が低下するようになる。これにより、第１室Ｃ１内においてデフレクタ５０の開口部８０では負圧が発生するようになる。その結果、図５に矢印Ｎにて示すように、第１室Ｃ１内において発生する負圧によって第２室Ｃ２内に存在するオイルが導入孔６０を通じて第１室Ｃ１に吸引されるようになる。尚、導入孔６０及び庇７０の個数、それらの配置位置、及びそれらの大きさは、開口部８０において適切な大きさの負圧が発生するように実験やシミュレーションを通じて設定されている。 Here, as shown in FIGS. 4 and 5, the deflector 50 is formed with the flange 70 of the above-described aspect, and therefore, in the first chamber C <b> 1, the front side in the rotation direction of the rotary shaft 2 by the same flange 70, The flow cross-sectional area of the air flow containing oil is reduced toward the downstream side in the air flow direction. For this reason, when the airflow containing oil passes the eaves 70, the flow velocity increases and the pressure decreases. Thereby, a negative pressure is generated in the opening 80 of the deflector 50 in the first chamber C1. As a result, as indicated by an arrow N in FIG. 5, the oil present in the second chamber C2 is sucked into the first chamber C1 through the introduction hole 60 due to the negative pressure generated in the first chamber C1. . Note that the number of introduction holes 60 and the ridges 70, their arrangement positions, and their sizes are set through experiments and simulations so as to generate an appropriate magnitude of negative pressure in the opening 80.
　ここで、開口部８０が回転軸２の回転方向前側、すなわち気流流れ方向の下流側に向けて開口するように庇７０が設けられているため、遠心力によって飛散したオイルがそのまま導入孔６０を通じて第２室Ｃ２に流出することが抑制される。 Here, since the flange 70 is provided so that the opening 80 opens toward the front side in the rotation direction of the rotary shaft 2, that is, toward the downstream side in the airflow direction, the oil scattered by the centrifugal force is directly passed through the introduction hole 60. Outflow to the second chamber C2 is suppressed.
　ところで、第２室Ｃ２や第１室Ｃ１からドレイン通路へ排出されるオイルがシールリテーナ４０の凹部４２内において一時的に滞留することがある。またこうして滞留するオイルの液面は、図３に一点鎖線にて示すように、デフレクタ５０の中心孔５３の縁部５２における最下部５２ａの直下まで到達し得る。そのため、導入孔及び庇を中心孔５３の縁部５２の鉛直方向における最下部５２ａよりも下側に形成しても、それら導入孔及び庇では前述したような負圧を発生させることができないおそれがある。 Incidentally, the oil discharged from the second chamber C2 or the first chamber C1 to the drain passage may temporarily stay in the recess 42 of the seal retainer 40. In addition, the level of the oil remaining in this way can reach the position immediately below the lowermost part 52a in the edge 52 of the center hole 53 of the deflector 50, as shown by a one-dot chain line in FIG. Therefore, even if the introduction hole and the ridge are formed below the lowermost portion 52a in the vertical direction of the edge 52 of the center hole 53, the introduction hole and the ridge may not be able to generate the negative pressure as described above. There is.
　この点、本実施形態によれば、導入孔６０及び庇７０の配置位置を的確に設定することができ、不要な導入孔及び庇を形成しなくとも済む。 In this respect, according to the present embodiment, the arrangement positions of the introduction hole 60 and the flange 70 can be accurately set, and unnecessary introduction holes and flanges need not be formed.
　また、導入孔及び庇の形成位置が回転軸２から離間するほど、庇に到達するまでにオイルを含む気流の流速が低下してしまい、開口部において発生する負圧が小さくなり、第２室Ｃ２内に存在するオイルを第１室Ｃ１に好適に吸引することができないおそれがある。 Further, the further away the formation position of the introduction hole and the soot from the rotary shaft 2, the lower the flow rate of the airflow including oil before reaching the soot, and the negative pressure generated in the opening becomes smaller, and the second chamber There is a possibility that the oil present in C2 cannot be suitably sucked into the first chamber C1.
　この点、本実施形態によれば、導入孔６０及び庇７０がデフレクタ５０の内周部５１に形成されているため、導入孔６０及び庇７０の配置位置が回転軸２に対して近接したものとなる。このため、流速が低下する前にオイルを含む気流が庇７０に到達するようになり、開口部８０において適切な大きさの負圧を発生させることができるようになる。従って、第２室Ｃ２内に存在するオイルを第１室Ｃ１に吸引することが好適にできるようになる。 In this regard, according to the present embodiment, since the introduction hole 60 and the flange 70 are formed in the inner peripheral portion 51 of the deflector 50, the arrangement positions of the introduction hole 60 and the flange 70 are close to the rotary shaft 2. It becomes. For this reason, before the flow velocity decreases, the airflow including oil reaches the ridge 70, and an appropriate amount of negative pressure can be generated in the opening 80. Therefore, the oil present in the second chamber C2 can be preferably sucked into the first chamber C1.
　以上説明した本実施形態に係る排気タービン過給機によれば、以下に示す効果が得られるようになる。 According to the exhaust turbine supercharger according to the present embodiment described above, the following effects can be obtained.
　（１）排気タービン過給機のデフレクタ５０は、同デフレクタ５０を貫通する導入孔６０と、同導入孔６０における回転軸２の回転方向後側の縁部（第１縁部）６１からスラストベアリング２０に向かって延びる庇７０と、を有している。庇７０は同回転軸２の回転方向前側ほどスラストベアリング２０寄りに位置している。また、導入孔６０における同回転軸２の回転方向前側の縁部（第２縁部）６２と庇７０とにより開口部８０が形成されている。こうした構成によれば、第２室Ｃ２内に滞留するオイルの量を低減することができ、シールリングカラー３０とシールリテーナ４０との間を通じてコンプレッサインペラ４側にオイルが漏出することを抑制することができるようになる。 (1) The deflector 50 of the exhaust turbine supercharger includes an introduction hole 60 penetrating the deflector 50 and an edge (first edge) 61 on the rear side in the rotation direction of the rotary shaft 2 in the introduction hole 60 from a thrust bearing. And a ridge 70 extending toward 20. The flange 70 is located closer to the thrust bearing 20 toward the front side in the rotational direction of the rotary shaft 2. Further, an opening 80 is formed by the edge (second edge) 62 and the flange 70 on the front side in the rotation direction of the rotation shaft 2 in the introduction hole 60. According to such a configuration, the amount of oil staying in the second chamber C2 can be reduced, and oil leakage to the compressor impeller 4 side through between the seal ring collar 30 and the seal retainer 40 can be suppressed. Will be able to.
　（２）導入孔６０及び庇７０はデフレクタ５０の周方向において複数配置されている。こうした構成によれば、デフレクタ５０の周方向における複数の位置に配置された開口部８０においてそれぞれ負圧が発生するようになる。これにより、第２室Ｃ２内において異なる位置に存在するオイルが各導入孔６０を通じて第１室Ｃ１に吸引されるようになる。従って、第２室Ｃ２内に滞留するオイルの量を的確に低減することができるようになる。 (2) A plurality of introduction holes 60 and ridges 70 are arranged in the circumferential direction of the deflector 50. According to such a configuration, a negative pressure is generated in each of the openings 80 arranged at a plurality of positions in the circumferential direction of the deflector 50. As a result, oil present at different positions in the second chamber C2 is sucked into the first chamber C1 through the respective introduction holes 60. Therefore, the amount of oil staying in the second chamber C2 can be accurately reduced.
　（３）導入孔６０及び庇７０は中心孔５３の縁部５２の鉛直方向における最下部５２ａよりも上側に配置されている。こうした構成によれば、導入孔６０及び庇７０の配置位置を的確に設定することができ、不要な導入孔及び庇を形成しなくとも済む。 (3) The introduction hole 60 and the flange 70 are disposed above the lowermost part 52 a in the vertical direction of the edge 52 of the center hole 53. According to such a configuration, the arrangement positions of the introduction hole 60 and the collar 70 can be set accurately, and unnecessary introduction holes and collars need not be formed.
　（４）デフレクタ５０は円板状をなすとともに中心孔５３を有する内周部５１と、同内周部５１よりもシールリテーナ４０寄りで且つ径方向外側に位置してシールリテーナ４０の内壁に当接する外周部５４とを有している。また、導入孔６０及び庇７０は内周部５１に形成されている。こうした構成によれば、流速が低下する前にオイルを含む気流を庇７０に到達させることができ、開口部８０において適切な大きさの負圧を発生させることができるようになる。従って、第２室Ｃ２内に存在するオイルを第１室Ｃ１に吸引することが好適にできるようになる。 (4) The deflector 50 has a disc shape and has an inner peripheral portion 51 having a center hole 53, and is positioned closer to the seal retainer 40 and radially outward than the inner peripheral portion 51, and contacts the inner wall of the seal retainer 40. And an outer peripheral portion 54 in contact therewith. In addition, the introduction hole 60 and the flange 70 are formed in the inner peripheral portion 51. According to such a configuration, an air stream containing oil can reach the ridge 70 before the flow velocity decreases, and a negative pressure of an appropriate magnitude can be generated in the opening 80. Therefore, the oil present in the second chamber C2 can be preferably sucked into the first chamber C1.
　（５）導入孔６０及び庇７０はデフレクタ５０をプレス加工することにより形成されている。こうした構成によれば、例えばデフレクタの本体に導入孔を形成した後、この本体に対して庇に対応する部材を溶着等にて形成する態様に比べて、デフレクタ５０を容易に形成することができるようになる。 (5) The introduction hole 60 and the flange 70 are formed by pressing the deflector 50. According to such a configuration, for example, after the introduction hole is formed in the main body of the deflector, the deflector 50 can be easily formed as compared with an aspect in which a member corresponding to the flange is formed on the main body by welding or the like. It becomes like this.
　尚、本発明に係る排気タービン過給機は、上記実施形態にて例示した構成に限定されるものではなく、これを適宜変更した例えば次のような形態として実施することもできる。 In addition, the exhaust turbine supercharger according to the present invention is not limited to the configuration exemplified in the above-described embodiment, and may be implemented as, for example, the following form appropriately modified.
　・導入孔６０、庇７０、及び開口部８０の形状は上記実施形態において例示したものに限られるものではない。例えば図６に示すように、導入孔２６０を略カップ状をなすものとし、庇２７０を曲面形状を有するものとし、開口部２８０を略半楕円状をなすものとしてもよい。またこの場合においても、導入孔２６０及び庇２７０をプレス加工により形成することが望ましい。 The shapes of the introduction hole 60, the flange 70, and the opening 80 are not limited to those illustrated in the above embodiment. For example, as shown in FIG. 6, the introduction hole 260 may have a substantially cup shape, the flange 270 may have a curved surface shape, and the opening 280 may have a substantially semi-elliptical shape. Also in this case, it is desirable to form the introduction hole 260 and the flange 270 by press working.
　・上記実施形態では、プレス加工によって導入孔及び庇７０を形成するようにしたが、本発明に係る庇の形成態様はこれに限られるものではない。他に例えばデフレクタの本体に導入孔を形成した後、この本体に対して庇に対応する部材を溶着等にて形成するようにしてもよい。 In the above embodiment, the introduction hole and the ridge 70 are formed by pressing, but the formation mode of the ridge according to the present invention is not limited to this. In addition, for example, after an introduction hole is formed in the main body of the deflector, a member corresponding to the flange may be formed on the main body by welding or the like.
　・上記実施形態では、デフレクタ５０の外周部５４が内周部５１よりもシールリテーナ４０寄りに位置するものとしたが、デフレクタの外周部が内周部よりもスラストベアリング２０寄りに位置するものを採用することもできる。この場合においても、上記実施形態と同様にして、導入孔及び庇を内周部に形成することが、開口部において適切な大きさの負圧を発生させる上では望ましい。 In the above embodiment, the outer peripheral portion 54 of the deflector 50 is positioned closer to the seal retainer 40 than the inner peripheral portion 51. However, the outer peripheral portion of the deflector is positioned closer to the thrust bearing 20 than the inner peripheral portion. It can also be adopted. Even in this case, it is desirable to form the introduction hole and the flange in the inner peripheral portion in the same manner as in the above-described embodiment in order to generate a negative pressure of an appropriate magnitude in the opening.
　・導入孔及び庇の個数、それらの配置位置、及びそれらの大きさは上記実施形態において例示したものに限られるものではなく、開口部において適切な大きさの負圧が発生するように実験等を通じて適宜変更することができる。例えば、導入孔及び庇を径方向において複数設けるようにしてもよい。 The number of introduction holes and ridges, their arrangement positions, and their sizes are not limited to those illustrated in the above embodiment, but experiments such that an appropriate negative pressure is generated at the opening, etc. Can be changed as appropriate. For example, a plurality of introduction holes and ridges may be provided in the radial direction.
　・上記実施形態では、気流流れ方向が回転軸２の回転方向に沿う位置に、導入孔６０及び庇７０を配置するようにした。しかしながら、気流流れ方向は、導入孔及び庇の配置位置が回転軸２の軸心に近接するほど回転軸２の回転方向から徐々に径方向に沿うようになる。そのため、例えば気流流れ方向が回転軸２の径方向に沿う位置に導入孔及び庇を配置する場合には、図７に示すように、デフレクタ３５０に対して導入孔３６０及び庇３７０を形成することが望ましい。すなわち、図７に示すように、庇３７０は、導入孔３６０における径方向内側の縁部３６１から紙面手前側、すなわちスラストベアリング２０に向かって延びるとともに同導入孔３６０における径方向外側ほどスラストベアリング２０寄りに位置している。また、開口部３８０は導入孔３６０における径方向外側の縁部３６２と庇３７０とにより形成されている。 In the above embodiment, the introduction hole 60 and the flange 70 are arranged at a position where the airflow direction is along the rotation direction of the rotary shaft 2. However, the airflow direction gradually follows the radial direction from the rotation direction of the rotation shaft 2 as the introduction position of the introduction hole and the flange approaches the axis of the rotation shaft 2. Therefore, for example, when the introduction hole and the ridge are arranged at a position where the airflow direction is along the radial direction of the rotary shaft 2, the introduction hole 360 and the ridge 370 are formed in the deflector 350 as shown in FIG. Is desirable. That is, as shown in FIG. 7, the flange 370 extends from the radially inner edge 361 of the introduction hole 360 toward the front side of the sheet, that is, toward the thrust bearing 20 and toward the radially outer side of the introduction hole 360 toward the thrust bearing 20. It is located near. The opening 380 is formed by a radially outer edge 362 and a flange 370 in the introduction hole 360.
　２…回転軸、４…コンプレッサインペラ、１０…ベアリングハウジング、２０…スラストベアリング、２１…スラストカラー、２１ａ…溝部、２２…スラストディスク、３０…シールリングカラー、３１…溝部、３２…突部、３９…シールリング、４０…シールリテーナ、４１…対向面、４２…凹部、４３…端面、５０，１５０，２５０，３５０…デフレクタ、５１…内周部、５２…縁部、５２ａ…最下部、５３，１５３…中心孔、５４…外周部、５５，１５５…舌片、６０，２６０，３６０…導入孔、６１…回転方向後側の縁部、６２…回転方向前側の縁部、７０，２７０…庇、８０，２８０、３８０…開口部、３６１…径方向内側の縁部、３６２…径方向外側の縁部。 DESCRIPTION OF SYMBOLS 2 ... Rotating shaft, 4 ... Compressor impeller, 10 ... Bearing housing, 20 ... Thrust bearing, 21 ... Thrust collar, 21a ... Groove, 22 ... Thrust disk, 30 ... Seal ring collar, 31 ... Groove, 32 ... Projection, 39 DESCRIPTION OF SYMBOLS ... Seal ring, 40 ... Seal retainer, 41 ... Opposite surface, 42 ... Recess, 43 ... End face, 50, 150, 250, 350 ... Deflector, 51 ... Inner periphery, 52 ... Edge, 52a ... Bottom, 53, 153 ... Center hole, 54 ... Outer peripheral part, 55, 155 ... Tongue piece, 60, 260, 360 ... Introduction hole, 61 ... Edge on the rear side in the rotational direction, 62 ... Edge on the front side in the rotational direction, 70, 270 ... 庇, 80, 280, 380... Opening, 361... Radially inner edge, 362.

Claims (7)

  1. 　排気のエネルギによってコンプレッサインペラを回転駆動する排気タービン過給機であって、
    　前記コンプレッサインペラの回転軸のスラスト力を受けるスラストベアリングと、
    　前記回転軸の軸線方向において前記スラストベアリングと前記コンプレッサインペラとの間に位置するとともに前記回転軸に外嵌されるシールリングカラーと、
    　前記シールリングカラーの外周面に対向する対向面を有するとともに同対向面にてシールリングを保持するシールリテーナと、
    　略円板状をなすとともに前記回転軸が挿通される中心孔を有するデフレクタであって前記シールリテーナと前記スラストベアリングとの間に形成される空間を２つの室に区画するデフレクタと、を備え、
    　前記２つの室のうち前記スラストベアリング側の室内において前記回転軸の回転に伴い発生する遠心力により飛散したオイルを含む気流の流れ方向を気流流れ方向と定義し、
    　前記デフレクタは、同デフレクタを貫通する導入孔と、同導入孔における前記気流流れ方向の上流側の縁部である第１縁部から前記スラストベアリングに向かって延びる庇と、を有し、
    　前記庇は前記気流流れ方向の下流側ほど前記スラストベアリング寄りに位置するように構成されるとともに、同庇は前記導入孔における前記気流流れ方向の下流側の縁部である第２縁部と共に当該下流側に向けて開口する開口部を形成する、排気タービン過給機。     An exhaust turbine supercharger that rotationally drives a compressor impeller by exhaust energy,
    A thrust bearing for receiving a thrust force of the rotating shaft of the compressor impeller;
    A seal ring collar that is positioned between the thrust bearing and the compressor impeller in the axial direction of the rotary shaft and is fitted on the rotary shaft;
    A seal retainer having a facing surface facing the outer peripheral surface of the seal ring collar and holding the seal ring on the facing surface;
    A deflector having a substantially disc shape and having a center hole through which the rotating shaft is inserted, and a space defining a space formed between the seal retainer and the thrust bearing in two chambers,
    The flow direction of the air flow including oil scattered by the centrifugal force generated with the rotation of the rotating shaft in the chamber on the thrust bearing side of the two chambers is defined as the air flow direction.
    The deflector has an introduction hole that penetrates the deflector, and a flange that extends from the first edge that is the upstream edge of the air flow direction in the introduction hole toward the thrust bearing.
    The scissors are configured to be positioned closer to the thrust bearing toward the downstream side in the airflow direction, and the scissors together with the second edge that is the downstream edge in the airflow direction in the introduction hole. An exhaust turbine supercharger that forms an opening that opens toward a downstream side.
  2. 　請求項１に記載の排気タービン過給機において、
    　前記第１縁部は前記導入孔における前記回転軸の回転方向後側の縁部であり、
    　前記第２縁部は前記導入孔における前記回転軸の回転方向前側の縁部であり、
    　前記庇は前記回転軸の回転方向前側ほど前記スラストベアリング寄りに位置する、排気タービン過給機。     In the exhaust turbine supercharger according to claim 1,
    The first edge is an edge on the rear side in the rotation direction of the rotation shaft in the introduction hole,
    The second edge is an edge on the front side in the rotation direction of the rotation shaft in the introduction hole,
    The soot is an exhaust turbine supercharger positioned closer to the thrust bearing toward the front side in the rotational direction of the rotating shaft.
  3. 　請求項１に記載の排気タービン過給機において、
    　前記第１縁部は前記導入孔における径方向内側の縁部であり、
    　前記第２縁部は前記導入孔における径方向外側の縁部であり、
    　前記庇は前記導入孔における径方向外側ほど前記スラストベアリング寄りに位置する、排気タービン過給機。     In the exhaust turbine supercharger according to claim 1,
    The first edge is a radially inner edge of the introduction hole,
    The second edge is a radially outer edge of the introduction hole,
    The soot is an exhaust turbine supercharger that is located closer to the thrust bearing toward the radially outer side of the introduction hole.
  4. 　請求項１～請求項３のいずれか一項に記載の排気タービン過給機において、
    　前記導入孔及び前記庇は前記デフレクタの周方向において複数配置されている、排気タービン過給機。     The exhaust turbine supercharger according to any one of claims 1 to 3,
    An exhaust turbine supercharger in which a plurality of the introduction holes and the soot are arranged in the circumferential direction of the deflector.
  5. 　請求項１～請求項４のいずれか一項に記載の排気タービン過給機において、
    　前記導入孔及び前記庇は前記中心孔の縁部の鉛直方向における最下部よりも上側に配置されている、排気タービン過給機。     The exhaust turbine supercharger according to any one of claims 1 to 4,
    The exhaust turbine supercharger, wherein the introduction hole and the soot are disposed above a lowermost portion in the vertical direction of an edge portion of the center hole.
  6. 　請求項１～請求項５のいずれか一項に記載の排気タービン過給機において、
    　前記デフレクタは円板状をなすとともに前記中心孔を有する内周部と、同内周部よりも前記シールリテーナ寄りで且つ径方向外側に位置する外周部とを有し、
    　前記導入孔及び前記庇は前記内周部に形成されている、排気タービン過給機。     The exhaust turbine supercharger according to any one of claims 1 to 5,
    The deflector has a disc shape and an inner peripheral portion having the center hole, and an outer peripheral portion located closer to the seal retainer and radially outward than the inner peripheral portion,
    The exhaust turbine supercharger, wherein the introduction hole and the soot are formed in the inner periphery.
  7. 　請求項１～請求項６のいずれか一項に記載の排気タービン過給機において、
    　前記導入孔及び前記庇は前記デフレクタをプレス加工することにより形成されている、排気タービン過給機。     The exhaust turbine supercharger according to any one of claims 1 to 6,
    The exhaust hole turbocharger, wherein the introduction hole and the soot are formed by pressing the deflector.
PCT/JP2012/057734 2012-03-26 2012-03-26 Exhaust turbine supercharger WO2013145078A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2012/057734 WO2013145078A1 (en) 2012-03-26 2012-03-26 Exhaust turbine supercharger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2012/057734 WO2013145078A1 (en) 2012-03-26 2012-03-26 Exhaust turbine supercharger

Publications (1)

Publication Number Publication Date
WO2013145078A1 true WO2013145078A1 (en) 2013-10-03

Family

ID=49258448

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2012/057734 WO2013145078A1 (en) 2012-03-26 2012-03-26 Exhaust turbine supercharger

Country Status (1)

Country Link
WO (1) WO2013145078A1 (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016079781A1 (en) * 2014-11-17 2016-05-26 三菱重工業株式会社 Turbomachine
WO2017080924A1 (en) * 2015-11-13 2017-05-18 Abb Turbo Systems Ag Device for sealing off a bearing housing, and exhaust-gas turbocharger having a device of said type
JPWO2017042925A1 (en) * 2015-09-10 2017-10-12 三菱重工業株式会社 Turbocharger bearing device and turbocharger
WO2019180428A1 (en) * 2018-03-20 2019-09-26 Cummins Ltd Bearing assembly for a turbomachine, and baffle element for the turbomachine
US10641330B2 (en) 2016-03-01 2020-05-05 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Bearing device and exhaust turbine supercharger

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03121275U (en) * 1990-03-27 1991-12-12
JPH07217440A (en) * 1994-02-02 1995-08-15 Taiho Kogyo Co Ltd Noncontact seal device for turbocharger
JPH0941982A (en) * 1995-07-28 1997-02-10 Taiho Kogyo Co Ltd Ring seal unit for turbocharger
JPH10339155A (en) * 1997-06-10 1998-12-22 Nippon Soken Inc Oil leak preventive device for supercharger
JP2004132319A (en) * 2002-10-11 2004-04-30 Nippon Soken Inc Lubricating device for turbocharger

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03121275U (en) * 1990-03-27 1991-12-12
JPH07217440A (en) * 1994-02-02 1995-08-15 Taiho Kogyo Co Ltd Noncontact seal device for turbocharger
JPH0941982A (en) * 1995-07-28 1997-02-10 Taiho Kogyo Co Ltd Ring seal unit for turbocharger
JPH10339155A (en) * 1997-06-10 1998-12-22 Nippon Soken Inc Oil leak preventive device for supercharger
JP2004132319A (en) * 2002-10-11 2004-04-30 Nippon Soken Inc Lubricating device for turbocharger

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106795808B (en) * 2014-11-17 2019-11-05 三菱重工发动机和增压器株式会社 Turbomachinery
CN106795808A (en) * 2014-11-17 2017-05-31 三菱重工业株式会社 Turbomachinery
JPWO2016079781A1 (en) * 2014-11-17 2017-06-29 三菱重工業株式会社 Turbo machine
EP3196437A4 (en) * 2014-11-17 2018-02-14 Mitsubishi Heavy Industries, Ltd. Turbomachine
WO2016079781A1 (en) * 2014-11-17 2016-05-26 三菱重工業株式会社 Turbomachine
US10605160B2 (en) 2014-11-17 2020-03-31 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Turbomachine
JPWO2017042925A1 (en) * 2015-09-10 2017-10-12 三菱重工業株式会社 Turbocharger bearing device and turbocharger
EP3249192A4 (en) * 2015-09-10 2018-08-01 Mitsubishi Heavy Industries, Ltd. Bearing device for turbocharger, and turbocharger
WO2017080924A1 (en) * 2015-11-13 2017-05-18 Abb Turbo Systems Ag Device for sealing off a bearing housing, and exhaust-gas turbocharger having a device of said type
CN108474266A (en) * 2015-11-13 2018-08-31 Abb涡轮***有限公司 Device for sealing bear box and the exhaust-driven turbo-charger exhaust-gas turbo charger with such device
CN108474266B (en) * 2015-11-13 2020-10-23 Abb涡轮***有限公司 Device for sealing a bearing housing and exhaust gas turbocharger having such a device
US10641330B2 (en) 2016-03-01 2020-05-05 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Bearing device and exhaust turbine supercharger
WO2019180428A1 (en) * 2018-03-20 2019-09-26 Cummins Ltd Bearing assembly for a turbomachine, and baffle element for the turbomachine

Similar Documents

Publication Publication Date Title
JP6250787B2 (en) Floating bush bearing device and turbocharger including the bearing device
JP6405473B2 (en) Turbocharger bearing device and turbocharger
EP3184834B1 (en) Oil draining device for thrust bearing and turbo charger provided with same
WO2013145078A1 (en) Exhaust turbine supercharger
US10281046B2 (en) Fluid machine having a labyrinth seal
RU2669424C2 (en) Device for generating a dynamic axial thrust to balance the overall axial thrust of a radial rotating machine
EP2913567B1 (en) Sealing device and rotating machine
KR20150013683A (en) Flinger oil seal and turbocharger incorporating the same
US9777576B2 (en) Drum seal
WO2017026292A1 (en) Bearing structure and supercharger
JP2003227344A (en) Turbocharger
US10865833B2 (en) Bearing structure and turbocharger
JP5281724B1 (en) Axial turbine for turbocharger
EP3409961B1 (en) Bearing device and exhaust turbine supercharger
JP2014125921A (en) Ball bearing unit for turbocharger
US20210102471A1 (en) Turbine and turbocharger
KR20090122880A (en) Thrust bearing seal for exhaust gas turbo charger
US11162386B2 (en) Turbocharger
JP2013087725A (en) Oil leakage prevention structure for supercharger
JP7501646B2 (en) Oil deflectors and turbochargers
JP5534165B2 (en) Oil seal
CN112041573B (en) Bearing and supercharger
JP6912003B2 (en) Centrifugal compressor
JPWO2017168642A1 (en) Impeller, rotating machine, turbocharger
JP2007154735A (en) Swirl prevention device for rotary machine

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12872635

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 12872635

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: JP