WO2014119195A1 - Palier pour turbocompresseur et turbocompresseur équipé de celui-ci - Google Patents

Palier pour turbocompresseur et turbocompresseur équipé de celui-ci Download PDF

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Publication number
WO2014119195A1
WO2014119195A1 PCT/JP2013/084680 JP2013084680W WO2014119195A1 WO 2014119195 A1 WO2014119195 A1 WO 2014119195A1 JP 2013084680 W JP2013084680 W JP 2013084680W WO 2014119195 A1 WO2014119195 A1 WO 2014119195A1
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WO
WIPO (PCT)
Prior art keywords
bearing
compressor
housing
turbocharger
shaft
Prior art date
Application number
PCT/JP2013/084680
Other languages
English (en)
Japanese (ja)
Inventor
覚 神原
Original Assignee
大豊工業株式会社
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 大豊工業株式会社 filed Critical 大豊工業株式会社
Publication of WO2014119195A1 publication Critical patent/WO2014119195A1/fr

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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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/22—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/08—Sliding-contact bearings for exclusively rotary movement for axial load only for supporting the end face of a shaft or other member, e.g. footstep 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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to a turbocharger bearing provided in an internal combustion engine and a technology of a turbocharger including the same.
  • a shaft (rotor shaft) is rotatably supported via a bearing disposed in a bearing housing (bearing housing).
  • a compressor housing is disposed on one side of the bearing housing, and a compressor (compressor impeller) connected to one end of the shaft by the compressor housing is included.
  • a turbine housing is disposed on the other side of the bearing housing, and a turbine (turbine impeller) connected to the other end of the shaft by the turbine housing is included.
  • the shaft in order to support the shaft in a well-balanced manner, the shaft is supported using a bearing that is formed long in the axial direction of the shaft. Further, as another known example, there is one in which the bearing is divided in the axial direction (two divisions) and the shaft is supported at two places.
  • the bearing is long in the axial direction of the shaft (in the case of divided bearings, the bearings are arranged at a predetermined interval). It is necessary to form a long bearing housing for supporting in the axial direction of the shaft. Therefore, it is difficult to reduce the size of the bearing housing, and thus it is difficult to reduce the size of the turbocharger.
  • the present invention has been made in view of the above circumstances, and the problem to be solved is that the end of the shaft can be rotatably supported in at least one of the compressor housing and the turbine housing. Is to provide a turbocharger bearing.
  • the turbocharger bearing of the present invention is a turbocharger that rotatably supports at least one of both end portions of a shaft connecting the compressor and the turbine arranged from the compressor-side housing to the turbine-side housing.
  • An outer peripheral portion that is fixed in the housing, a sliding portion that rotatably supports an end portion of the shaft, and the outer peripheral portion and the sliding portion are connected to each other, and the sliding portion And a connecting portion that supports.
  • the connecting portion is formed by a plurality of rod-like portions arranged at intervals.
  • the cross-sectional shape of the connecting portion is formed such that the length in the flow direction of the air flowing through the turbocharger is longer than the length in the direction perpendicular to the flow direction. Is.
  • the cross-sectional shape of the connecting portion is formed to be a streamline type.
  • the outer peripheral portion is formed in an annular shape along the inner surface of the housing.
  • a turbocharger according to the present invention comprises the turbocharger bearing according to any one of claims 1 to 5.
  • the end of the shaft can be rotatably supported in at least one of the compressor side housing and the turbine side housing.
  • turbocharger bearing of the present invention it is possible to secure a space for air to flow between the connecting portions, and it is possible to suppress a decrease in the efficiency of the turbocharger due to the turbocharger bearing hindering the air flow. it can.
  • turbocharger bearing it is possible to facilitate air circulation while ensuring the strength of the turbocharger bearing.
  • the turbocharger bearing of the present invention can be more stably fixed in the housing.
  • the end of the shaft can be rotatably supported in at least one of the compressor side housing and the turbine side housing.
  • the front-rear direction, the up-down direction, and the left-right direction are defined according to the arrows shown in the figure.
  • the turbocharger 10 sends compressed air to the cylinder 2 of the engine. Air is supplied to the cylinder 2 through the intake passage 1. The air passes through an air cleaner 4, a turbocharger 10, an intercooler 5, and a throttle valve 6 arranged in the middle of the intake passage 1 in order, and is supplied to the cylinder 2. At this time, since the air is compressed by the compressor 100 of the turbocharger 10, more air can be fed into the cylinder 2.
  • the exhaust passage 3 is divided and a passage that does not pass through the turbine 120 is separately formed.
  • the passage can be opened and closed by a waste gate valve 7.
  • the waste gate valve 7 is driven to open and close by an actuator 8.
  • the operation of the actuator 8 is controlled by a negative pressure generating mechanism 9 composed of an electromagnetic valve or the like.
  • the turbocharger 10 mainly includes a compressor housing 20, a turbine housing 40, a bearing housing 60, a shaft 80, a compressor 100, a turbine 120, a center journal bearing 140, a turbine side thrust bearing 160, and a compressor side journal thrust bearing 180.
  • a compressor housing 20 shown in FIG. 2 is an embodiment of a housing (compressor-side housing) according to the present invention, and forms a part of an intake passage 1 (see FIG. 1) and contains a compressor 100. It is.
  • the compressor housing 20 mainly includes a first compressor housing 21 and a second compressor housing 22.
  • the first compressor housing 21 constitutes a front portion of the compressor housing 20.
  • the first compressor housing 21 is formed in a substantially box shape with the rear opened.
  • An intake port 21 a is formed in the first compressor housing 21.
  • the intake port 21 a is a through hole that communicates the inside and the outside of the first compressor housing 21.
  • the intake port 21 a is formed on the front side surface of the first compressor housing 21.
  • the intake port 21a is formed such that its axis is directed in the front-rear direction.
  • the air inlet 21a is formed so as to be substantially circular when viewed in cross section (viewed from the front-rear direction).
  • the second compressor housing 22 constitutes the rear part of the compressor housing 20.
  • the second compressor housing 22 is formed in a substantially plate shape.
  • the second compressor housing 22 is appropriately fixed to the rear portion of the first compressor housing 21 so as to close the opened rear portion of the first compressor housing 21.
  • the turbine housing 40 is an embodiment of a housing (a turbine-side housing) according to the present invention, and forms a part of the exhaust passage 3 (see FIG. 1) and includes the turbine 120.
  • the turbine housing 40 is formed in a substantially box shape.
  • the turbine housing 40 is disposed behind the compressor housing 20, and is fixed to the compressor housing 20 (more specifically, the second compressor housing 22) using a fastening band 50.
  • An exhaust port 40 a is formed in the turbine housing 40.
  • the exhaust port 40 a is a through-hole that communicates the inside and the outside of the turbine housing 40.
  • the exhaust port 40 a is formed on the rear side surface of the turbine housing 40.
  • the exhaust port 40a is formed such that its axis is directed in the front-rear direction.
  • the exhaust port 40 a is formed on the same axis as the intake port 21 a of the compressor housing 20.
  • the exhaust port 40a is formed so as to be substantially circular when viewed in cross section (viewed in the front-rear direction).
  • the bearing housing 60 supports the compressor 100 and the turbine 120 via a shaft 80 described later.
  • the bearing housing 60 is formed in a substantially box shape. Compared to the compressor housing 20 and the turbine housing 40, it is formed in a substantially box shape that is small.
  • the bearing housing 60 is disposed between the compressor housing 20 and the turbine housing 40 and is fixed in a space surrounded by the compressor housing 20 and the turbine housing 40.
  • the bearing housing 60 is formed with a bearing portion 60a, an oil supply hole 60b, and an oil discharge hole 60c.
  • the bearing portion 60a is a through hole that communicates the bearing housing 60 in the front-rear direction.
  • the bearing portion 60a is formed such that its axis is directed in the front-rear direction.
  • the bearing portion 60 a is formed on the same axis as the intake port 21 a of the compressor housing 20 and the exhaust port 40 a of the turbine housing 40.
  • the bearing portion 60a is formed so as to be substantially circular when viewed in cross section (viewed from the front-rear direction).
  • the oil supply hole 60b is for supplying lubricating oil to the bearing portion 60a.
  • the oil supply hole 60b is formed so as to communicate with the outer peripheral surface of the bearing housing 60 and the bearing portion 60a (more specifically, the front and rear intermediate portions of the bearing portion 60a).
  • the oil drain hole 60c is for discharging the lubricating oil that has lubricated the bearing portion 60a to the outside.
  • the oil drain hole 60c is formed to communicate the outer peripheral surface of the bearing housing 60 and the bearing portion 60a (more specifically, the end portion of the bearing portion 60a).
  • the shaft 80 is formed in a substantially cylindrical shape, and is arranged with its longitudinal direction facing the front-rear direction.
  • the shaft 80 is inserted into the bearing portion 60 a of the bearing housing 60.
  • One end (front end) of the shaft 80 extends into the compressor housing 20.
  • the other end (rear end) of the shaft 80 extends into the turbine housing 40.
  • a shaft 81 is provided with a collar 81.
  • the shaft 80 is formed with a first engagement portion 80a.
  • the collar 81 is a substantially cylindrical member that is fitted on the shaft 80.
  • the collar 81 is fixed to an intermediate part in the front and rear of the shaft 80 (rear of the compressor housing 20).
  • the third is a concave portion (concave portion) formed on the front end surface of the shaft 80.
  • the first engaging portion 80a is formed in a substantially conical shape.
  • the apex (conical apex) of the first engagement portion 80 a is formed so as to be located on the axis of the shaft 80.
  • the compressor 100 is an impeller for compressing air.
  • the compressor 100 is disposed in the compressor housing 20 so as to face the intake port 21a.
  • the compressor 100 is fixed to one end (front end) of the shaft 80.
  • the turbine 120 is an impeller for converting the motion of air (fluid) into its own rotational motion.
  • the turbine 120 is disposed in the turbine housing 40 so as to face the exhaust port 40a.
  • the turbine 120 is formed integrally with the other end (rear end) of the shaft 80.
  • the center journal bearing 140 supports the shaft 80 so that it can rotate smoothly.
  • the center journal bearing 140 is constituted by a cylindrical slide bearing.
  • the center journal bearing 140 is disposed in the bearing portion 60a of the bearing housing 60 with its longitudinal direction facing the front-rear direction.
  • a shaft 80 is inserted through the center journal bearing 140.
  • the center journal bearing 140 is interposed between the shaft 80 and the bearing housing 60.
  • the turbine-side thrust bearing 160 is a member that receives axial force (force from the front to the rear) applied to the shaft 80.
  • the turbine side thrust bearing 160 is interposed between the collar 81 provided on the shaft 80 and the bearing housing 60.
  • a compressor-side journal thrust bearing 180 shown in FIGS. 2 and 3 is an embodiment of a turbocharger bearing according to the present invention, and supports the shaft 80 so that it can rotate smoothly.
  • the compressor-side journal thrust bearing 180 mainly includes an outer peripheral portion 181, a rib 182, and a sliding portion 183.
  • the outer peripheral portion 181 is a portion formed in an annular shape when viewed from the front.
  • the diameter of the outer peripheral surface of the outer peripheral portion 181 is formed to be substantially the same as the inner diameter of the intake port 21 a of the compressor housing 20. Accordingly, the outer peripheral portion 181 has a shape along the inner surface of the compressor housing 20 (the inner surface of the intake port 21a).
  • the connecting portion 3 is an embodiment of the connecting portion according to the present invention, and is a rod-like portion extending from the inner peripheral surface of the outer peripheral portion 181 toward the central portion of the outer peripheral portion 181.
  • the ribs 182 extend from a plurality of locations (three locations in the present embodiment) on the inner peripheral surface of the rib 182 toward the center of the outer peripheral portion 181.
  • the ribs 182 are arranged at equal intervals from each other (in this embodiment, 120 ° in front view).
  • the cross-sectional shape of the rib 182 is formed to be long in the front-rear direction. Specifically, the cross-sectional shape of the rib 182 is formed such that the length L in the front-rear direction is longer than the width W in the left-right direction.
  • the rib 182 has a cross-sectional shape that is formed so that its front end is relatively wide and narrows toward the rear, so-called streamline type (air flowing around the rib 182 is vortex or turbulent). (Or a shape that does not easily occur).
  • the sliding part 183 is a substantially circular plate-like part formed at the center of the outer peripheral part 181.
  • the sliding portion is supported by the rib 182.
  • a second engaging portion 183 a is formed on the sliding portion 183.
  • the second engaging portion 183a is a convex portion (convex portion) formed on the rear side surface of the sliding portion 183.
  • the second engaging portion 183a is formed in a substantially conical shape.
  • the compressor-side journal thrust bearing 180 configured as described above is disposed in front of the shaft 80 in the air inlet 21 a of the compressor housing 20.
  • the second engagement portion 183a of the compressor-side journal thrust bearing 180 is engaged with the first engagement portion 80a by being inserted into the first engagement portion 80a of the shaft 80.
  • the compressor-side journal thrust bearing 180 is appropriately fixed to the inner diameter portion of the intake port 21a of the compressor housing 20.
  • the turbine 120 is rotated by the exhaust from the cylinder 2 of the engine, and the exhaust is discharged through the exhaust port 40 a of the turbine housing 40.
  • the rotation of the turbine 120 is transmitted to the compressor 100 via the shaft 80.
  • the air supplied from the intake port 21a of the compressor housing 20 can be compressed, and the compressed air can be sent to the cylinder 2 of the engine.
  • the air flowing from the front to the rear through the intake port 21a of the compressor housing 20 is divided into three spaces S defined by the outer peripheral portion 181, the rib 182 and the sliding portion 183 of the compressor-side journal thrust bearing 180 (FIG. 3). Reference) can be distributed. Moreover, since the cross-sectional shape of the rib 182 is streamlined, air can easily flow through the compressor-side journal thrust bearing 180 (see the white arrow in FIG. 4).
  • a load applied in the axial direction of the shaft 80 is supported by the turbine side thrust bearing 160 and the compressor side journal thrust bearing 180. More specifically, the load applied to the shaft 80 from the front to the rear is supported by the turbine side thrust bearing 160, and the load applied to the shaft 80 from the rear to the front is supported by the compressor side journal thrust bearing 180.
  • the load applied in the radial direction of the shaft 80 (direction perpendicular to the axis) is supported by the center journal bearing 140 and the compressor-side journal thrust bearing 180.
  • the shaft 80 can be supported stably without being inclined. .
  • the shaft 80 can be supported only by supporting the middle portion of the shaft 80 with one short bearing (center journal bearing 140). Can be stably supported. This eliminates the need to support the middle part of the shaft 80 with a plurality of bearings or a bearing that is long in the longitudinal direction. Therefore, the structure for supporting the middle part of the shaft 80 (that is, the center journal bearing 140 and The bearing housing 60) for supporting the center journal bearing 140 can be reduced in size and weight, and as a result, the entire turbocharger 10 can be reduced in size and weight. Along with this, the cost can be reduced.
  • the shaft 80 is supported by the center journal bearing 140 and the compressor side journal thrust bearing 180 so as to be smoothly rotatable.
  • Lubricating oil is supplied to the center journal bearing 140 through an oil supply hole 60b of the bearing housing 60.
  • the lubricating oil lubricates and cools the sliding surface between the bearing portion 60 a and the center journal bearing 140 and the sliding surface between the center journal bearing 140 and the shaft 80.
  • the lubricating oil that has lubricated and cooled the portion is discharged from the end portion of the bearing portion 60a to the outside through the oil drain hole 60c.
  • the compressor-side journal thrust bearing 180 supports the shaft 80 by engaging the second engagement portion 183a with the first engagement portion 80a of the shaft 80.
  • the above-mentioned center journal bearing 140 is slidably in contact with the outer peripheral surface of the shaft 80, whereas the compressor-side journal thrust bearing 180 is on the axis of the shaft 80 (or a point close to the axis). It will slidably contact the inner peripheral surface of the first engaging portion 80a.
  • the rotation radius (distance from the axis of the shaft 80) of the portion where the shaft 80 and the compressor-side journal thrust bearing 180 are in contact is 0 (or a value close to 0).
  • the peripheral speed (relative speed) at the portion where the shaft 80 and the compressor-side journal thrust bearing 180 are in contact with each other is 0 at the apex of the second engagement portion 183a (other portions of the second engagement portion 183a). (Small value close to 0 in the portion). Therefore, it is possible to suppress friction at a portion where the shaft 80 and the compressor-side journal thrust bearing 180 are in contact with each other.
  • the wear resistance and seizure resistance of the part can be improved, and at the same time, the transient performance and the turbo efficiency can be improved by reducing the friction torque loss.
  • the supply amount of the lubricating oil to the support portion (the center journal bearing 140 and the compressor side journal thrust bearing 180) of the shaft 80 can be reduced as a whole, the stirring resistance of the lubricating oil can be reduced, As a result, mechanical loss can be reduced and turbo efficiency can be improved.
  • the compressor-side journal thrust bearing 180 is disposed in the intake port 21a of the compressor housing 20, it is cooled by the air supplied to the turbocharger 10 through the intake port 21a. Accordingly, it is not necessary to separately provide a mechanism for cooling the sliding portion 183 of the compressor side journal thrust bearing 180 (even if it is provided, a large cooling capacity is not necessary, so the configuration can be simplified).
  • the compressor-side journal thrust bearing 180 (turbocharger bearing) according to the present embodiment is arranged from the compressor housing 20 (compressor-side housing) to the turbine housing 40 (turbine-side housing).
  • a compressor-side journal thrust bearing 180 that rotatably supports one end portion (front end portion) of the shaft 80 that connects the turbine 120 and the end portion of the shaft 80.
  • a rib 182 (connecting portion) that connects the outer peripheral portion 181 and the sliding portion 183 and supports the sliding portion 183.
  • the end of the shaft 80 can be rotatably supported in the compressor housing 20.
  • the overall length of the center journal bearing 140 (bearing) provided in the middle portion of the shaft 80 can be shortened, and as a result, the bearing housing 60 (housing) for supporting the center journal bearing 140 can be reduced in size. .
  • the rib 182 is formed by a plurality of rod-like portions arranged at intervals.
  • the cross-sectional shape of the rib 182 is such that the length (length L) in the flow direction (front-rear direction) of the air flowing through the turbocharger 10 is the length (width) in the direction (left-right direction) perpendicular to the flow direction. It is formed so as to be longer than W).
  • cross-sectional shape of the rib 182 is formed to be a streamline type.
  • This configuration makes it easier to circulate air.
  • outer peripheral portion 181 is formed in an annular shape along the inner surface of the compressor housing 20.
  • the compressor-side journal thrust bearing 180 can be more stably fixed in the compressor housing 20.
  • turbocharger 10 includes the above-described compressor-side journal thrust bearing 180.
  • the end of the shaft 80 can be rotatably supported in the compressor housing 20.
  • the outer peripheral portion 181 of the compressor-side journal thrust bearing 180 is annular, but the present invention is not limited to this, and the outer peripheral portion 181 is in the housing (compressor housing 20). Any shape can be used as long as the shape can be fixed to.
  • the cross-sectional shape of the rib 182 is streamlined, but the present invention is not limited to this, and may be an arbitrary shape.
  • three ribs 182 are provided to support the sliding portion 183.
  • the present invention is not limited to this, and the sliding portion 183 can be supported. If there is, the number is not limited.
  • the ribs 182 are arranged at equal intervals.
  • the present invention is not limited to this, and the ribs 182 can be arranged at different intervals.
  • the second embodiment (see FIG. 5) of the present invention is different from the first embodiment (see FIG. 3) in that the first engaging portion 80a of the shaft 80 is formed in a substantially conical convex shape, and the compressor side journal thrust is made.
  • the second engaging portion 183a formed on the sliding portion 183 of the bearing 180 is formed in a substantially conical concave shape.
  • first engagement portion 80a and the second engagement portion 183a are convex and the other is concave, either may be convex (concave).
  • the third embodiment of the present invention is different from the first embodiment (see FIG. 3) in that the first engaging portion 80a of the shaft 80 is formed into a substantially cylindrical convex shape, and the compressor side journal thrust is made.
  • the second engagement portion 183a formed on the sliding portion 183 of the bearing 180 is formed in a substantially cylindrical concave shape.
  • the shape is not limited to a substantially conical shape.
  • the shape which combined the cylinder and the cone shape which formed the cone-shaped part in the front-end
  • tip part of a cylinder etc. may be sufficient.
  • the fourth embodiment (see FIG. 7) of the present invention is different from the first embodiment (see FIG. 2) in that a turbine-side journal thrust bearing 200 is provided instead of the compressor-side journal thrust bearing 180. .
  • the turbine side journal thrust bearing 200 has substantially the same shape as the compressor side journal thrust bearing 180 according to the first embodiment.
  • the turbine-side journal thrust bearing 200 is different from the compressor-side journal thrust bearing 180 in that the cross-sectional shape of the rib (the portion corresponding to the rib 182 of the compressor-side journal thrust bearing 180) matches the air flow direction and the shaft 80 side.
  • the (front side) width is relatively wide.
  • the turbine side journal thrust bearing 200 is fixed to the inner diameter portion of the exhaust port 40a of the turbine housing 40, and rotatably supports the rear end of the shaft 80 (similar to the compressor side journal thrust bearing 180 according to the first embodiment). .
  • the fifth embodiment (see FIG. 8) of the present invention is different from the first embodiment (see FIG. 2) in that a turbine-side journal thrust bearing 200 is provided in addition to the compressor-side journal thrust bearing 180. .
  • the shaft 80 is rotatably supported by the compressor side journal thrust bearing 180 and the turbine side journal thrust bearing 200 at both ends thereof.
  • the center journal bearing 140 (see FIG. 2) supporting the middle portion of the shaft 80 may be abolished, and the bearing housing 60 (see FIG. 2) supporting the center journal bearing 140 may be abolished.
  • the turbocharger 1 can be reduced in size.
  • a center plate 220 that isolates the internal space of the compressor housing 20 and the internal space of the turbine housing 40 is provided.
  • the present invention is applicable to a turbocharger bearing provided in an internal combustion engine and a turbocharger including the same.
  • Turbocharger 20 Compressor housing (housing) 40 Turbine housing (housing) 80 Shaft 100 Compressor 120 Turbine 180 Compressor side journal thrust bearing (turbocharger bearing) 181 outer peripheral part 182 rib (connecting part) 183 Sliding part

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

La présente invention concerne un palier destiné à un turbocompresseur avec lequel la partie d'extrémité d'un arbre peut être supportée en rotation à l'intérieur du boîtier de compresseur et/ou du boîtier de turbine. Un palier lisse de butée (180) côté compresseur, qui est agencé à travers l'intérieur du boîtier de compresseur et du boîtier de turbine et supporte en rotation une partie d'extrémité (la partie d'extrémité avant) d'un arbre (80) reliant le compresseur et la turbine, comprend : une pièce circonférentielle externe (181) ancrée à l'intérieur du boîtier de compresseur ; une pièce coulissante (183) supportant en rotation la partie d'extrémité de l'arbre (80) ; et des nervures (182) reliant la pièce circonférentielle externe (181) et la pièce coulissante (183), ce qui permet de supporter la pièce coulissante (183).
PCT/JP2013/084680 2013-01-30 2013-12-25 Palier pour turbocompresseur et turbocompresseur équipé de celui-ci WO2014119195A1 (fr)

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JP2013-014924 2013-01-30
JP2013014924A JP5995736B2 (ja) 2013-01-30 2013-01-30 ターボチャージャ用軸受及びそれを具備するターボチャージャ

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WO2014119195A1 true WO2014119195A1 (fr) 2014-08-07

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2480095A (en) * 1946-01-21 1949-08-23 Buchi Alfred Shaft and bearing arrangement
US7571607B2 (en) * 2006-03-06 2009-08-11 Honeywell International Inc. Two-shaft turbocharger

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