WO2022181510A1 - ガス軸受装置及びターボチャージャ - Google Patents
ガス軸受装置及びターボチャージャ Download PDFInfo
- Publication number
- WO2022181510A1 WO2022181510A1 PCT/JP2022/006818 JP2022006818W WO2022181510A1 WO 2022181510 A1 WO2022181510 A1 WO 2022181510A1 JP 2022006818 W JP2022006818 W JP 2022006818W WO 2022181510 A1 WO2022181510 A1 WO 2022181510A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rotating shaft
- pair
- snap rings
- housing
- bearing device
- Prior art date
Links
- 239000011888 foil Substances 0.000 claims abstract description 44
- 239000012530 fluid Substances 0.000 claims abstract description 5
- 230000002093 peripheral effect Effects 0.000 claims description 22
- 239000000463 material Substances 0.000 claims description 9
- 229920003002 synthetic resin Polymers 0.000 claims description 6
- 239000000057 synthetic resin Substances 0.000 claims description 6
- 238000010586 diagram Methods 0.000 description 5
- 238000013016 damping Methods 0.000 description 2
- 229920006351 engineering plastic Polymers 0.000 description 2
- 229920006324 polyoxymethylene Polymers 0.000 description 2
- 239000004677 Nylon Substances 0.000 description 1
- 229930182556 Polyacetal Natural products 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 229920001778 nylon Polymers 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
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
- F02B39/02—Drives of pumps; Varying pump drive gear ratio
- F02B39/08—Non-mechanical drives, e.g. fluid drives having variable gear ratio
- F02B39/10—Non-mechanical drives, e.g. fluid drives having variable gear ratio electric
-
- 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
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
- F16C17/024—Sliding-contact bearings for exclusively rotary movement for radial load only with flexible leaves to create hydrodynamic wedge, e.g. radial foil bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
- F16C17/026—Sliding-contact bearings for exclusively rotary movement for radial load only with helical grooves in the bearing surface to generate hydrodynamic pressure, e.g. herringbone grooves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/02—Sliding-contact bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
- F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
- F16C2226/50—Positive connections
- F16C2226/70—Positive connections with complementary interlocking parts
- F16C2226/74—Positive connections with complementary interlocking parts with snap-fit, e.g. by clips
-
- 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
- F16C2300/00—Application independent of particular apparatuses
- F16C2300/20—Application independent of particular apparatuses related to type of movement
- F16C2300/22—High-speed rotation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/23—Gas turbine engines
- F16C2360/24—Turbochargers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/02—Shafts; Axles
- F16C3/023—Shafts; Axles made of several parts, e.g. by welding
Definitions
- the present disclosure relates to gas bearing devices and turbochargers.
- This application claims priority based on Japanese Patent Application No. 2021-030501 filed with the Japan Patent Office on February 26, 2021, the content of which is incorporated herein.
- Patent Document 1 a ring-shaped top foil in which a rotatable cylindrical rotating shaft is passed inside and the inner peripheral surface is spaced from the outer peripheral surface of the rotating shaft, and a top foil is provided on the outer periphery and rotates.
- a gas bearing device includes a damping member that damps vibration in a direction that intersects the axis of a rotating shaft inside, and a ring-shaped housing that is provided on the outer periphery of the damping member.
- the present disclosure has been made in view of the above-described problems, and aims to provide a gas bearing device and a turbocharger that can suppress the temperature rise of the top foil due to mechanical loss during rotation of the rotating shaft.
- the gas bearing device is A gas bearing device using gas as a working fluid, a rotating shaft; a housing through which the rotating shaft passes; an annular top foil provided inside the housing and surrounding the outer periphery of the rotating shaft; a back spring provided between the top foil and the housing, and having a plurality of peaks contacting the top foil and a plurality of valleys contacting the housing; a pair of snap rings fitted in a shaft hole through which the rotating shaft of the housing passes, and restricting movement of the back spring in the axial direction of the rotating shaft; with At least one of the pair of snap rings or a region of the rotating shaft facing at least one of the pair of snap rings has a turning groove inclined with respect to the axis of the rotating shaft.
- the gas bearing device of the present disclosure when the rotating shaft rotates, air is introduced between the rotating shaft and the top foil, and the rotating shaft and the top foil are cooled. It is possible to suppress the temperature rise of the top foil due to loss.
- FIG. 1 is a cross-sectional view schematically showing the configuration of a turbocharger in which a gas bearing device according to an embodiment is built;
- FIG. 2 is a longitudinal sectional view schematically showing the configuration of the gas bearing device shown in FIG. 1;
- FIG. 3 is a cross-sectional view schematically showing the configuration of the gas bearing device shown in FIG. 2;
- 3 is a front view of the snap ring shown in FIG. 2;
- FIG. FIG. 4B is a transverse sectional view (AA sectional view) of the snap ring shown in FIG. 4-1;
- FIG. 4 is a view (cross-sectional view) showing an example in which both of a pair of snap rings are provided with turning grooves inclined with respect to the axis of the rotating shaft;
- FIG. 10 is a view (cross-sectional view) showing an example in which a rotating shaft is provided with a turning groove that is inclined with respect to the axis of the rotating shaft.
- FIG. 4 is a diagram (cross-sectional view) conceptually showing the relationship between the snap ring and the back spring, showing a state before the rotating shaft is installed.
- FIG. 4 is a view (cross-sectional view) conceptually showing the relationship between the snap ring and the back spring, showing a state during low-speed rotation of the rotating shaft.
- FIG. 4 is a diagram (cross-sectional view) conceptually showing the relationship between the snap ring and the back spring, showing a state when the rotating shaft rotates at medium speed. It is a figure for demonstrating the support rigidity of a back spring.
- FIG. 1 is a longitudinal sectional view schematically showing the configuration of a turbocharger 1 incorporating a gas bearing device 10 according to an embodiment.
- the turbocharger 1 incorporating the gas bearing device 10 according to the embodiment is mounted on, for example, an automobile engine.
- the turbocharger 1 includes a turbine 3 that rotates with the flow of exhaust gas, and a compressor 5 that takes in and compresses air as the turbine 3 rotates.
- the turbine 3 has a turbine housing 31 and turbine rotor blades 33 (turbine impeller) rotatably housed in the turbine housing 31, and the compressor 5 has a compressor housing 51 and a compressor housing 51 rotatably. and a housed impeller 53 (compressor impeller).
- Each of the turbine housing 31 and the compressor housing 51 is fixed to a bearing housing 71 in which the gas bearing device 10 is built by fastening members (for example, bolts). They are interconnected by a rotary shaft 91 passing through the bearing device 10). Therefore, the turbine rotor blades 33, the impeller 53 and the rotating shaft 91 are arranged on the same axis line AXL.
- the turbine rotor blades 33 are rotated, for example, by exhaust gas discharged from an automobile engine, which causes the impeller 53 to rotate via a rotating shaft 91, thereby supplying air to the automobile engine. Compressed.
- the turbine housing 31 is composed of a cylindrical portion 31a (shroud portion) that houses the turbine rotor blades 33, and a scroll portion 31b that surrounds a portion of the cylindrical portion 31a on the bearing housing 71 side.
- the scroll portion 31b has an exhaust gas inlet (not shown) and communicates with the cylindrical portion 31a through a throat portion 31c.
- An opening of the cylindrical portion 31a on the side opposite to the bearing housing 71 forms an exhaust gas outlet 31d.
- An end wall 75 (turbine-side end wall) of the bearing housing 71 is fitted into the opening of the turbine housing 31 on the bearing housing 71 side.
- An end wall 75 of the bearing housing 71 is fastened to one end of a cylindrical peripheral wall 73 (bearing housing main body) by a fastening member (for example, a bolt), and constitutes a part (end wall 75) of the bearing housing 71. do.
- a seal portion 751 is provided in the end wall 75 , a seal hole is formed in the seal portion 751 so as to penetrate through the center of the end wall 75 , and the rotating shaft 91 is arranged in the seal portion 751 .
- the compressor housing 51 is composed of a cylindrical portion 51a (shroud portion) that houses the impeller 53, and a scroll portion 51b that surrounds the portion of the cylindrical portion 51a on the bearing housing 71 side.
- the scroll portion 51b has an air supply outlet (not shown) and communicates with the cylindrical portion 51a through the diffuser portion 51c.
- An opening of the cylindrical portion 51a on the side opposite to the bearing housing 71 forms an inlet 51d for supplying air.
- An end wall 77 (compressor-side end wall) of the bearing housing 71 is fitted into the opening of the compressor housing 51 on the bearing housing 71 side.
- An end wall 77 of the bearing housing 71 is fastened to the other end of the peripheral wall 73 (bearing housing main body) with a fastening member (for example, a bolt), and constitutes a part of the bearing housing 71 (end wall 77).
- An annular seal portion 771 is fitted to the end wall 77 .
- a seal hole is formed through the center of the seal portion 771 , and the rotating shaft 91 is arranged in the seal portion 771 .
- bearing portions 76 and 78 are provided on a turbine-side end wall 75 and a compressor-side end wall 77, respectively, and bearing holes 761 and 781 are formed in the bearing portions 76 and 78, respectively.
- the gas bearing device 10 according to the present embodiment is arranged as a radial bearing in each of the bearing holes 761 and 781, and the rotating shaft 91 passes through each of the bearing holes of the bearing portions 76 and 78 while passing through each of the gas bearing devices 10. 761,781.
- the rotating shaft 91 has a pair of shaft portions 91a and 91b, an intermediate portion 91c, a turbine rotor blade attachment portion 91d, and a compressor impeller attachment portion 91e.
- the pair of shaft portions 91a and 91b are portions arranged in the shaft holes of the bearing portions 76 and 78 while passing through the gas bearing devices 10, and extend into the seal portions 751 and 773, respectively.
- the intermediate portion 91c is provided between the pair of shaft portions 91a and 91b, has a larger diameter than the pair of shaft portions 91a and 91b, and has a step at the boundary between the pair of shaft portions 91a and 91b.
- the turbine rotor blade attachment portion 91d is a portion provided at the end portion on the turbine 3 side, has a smaller diameter than the shaft portion 91a, and has a step with the shaft portion 91a.
- the compressor impeller attachment portion 91e is a portion provided at the end portion on the compressor 5 side, and has a smaller diameter than the shaft portion 91b and a step between the shaft portion 91b and the turbine rotor blade attachment portion 91d. ing.
- the turbine rotor blade 33 consists of a hub 33a and a plurality of blades 33b.
- the hub 33a has a rotationally symmetrical shape about the axis AXL.
- One end of the hub 33a is located on the exhaust gas outlet side in the direction along the axis AXL, and the other end of the hub 33a is located on the bearing housing 71 side.
- the outer peripheral surface of the hub 33a has a trumpet shape that expands from one end side toward the other end side, and the hub 33a has a rear surface facing the bearing housing 71 on the other end side.
- the hub 33a is provided with mounting holes 33a1 passing through the hub 33a along the axis AXL, and the mounting holes 33a1 are open at both ends of the hub 33a.
- the plurality of blades 33b are integrally attached to the outer peripheral surface of the hub 33a and arranged at predetermined intervals in the circumferential direction of the hub 33a.
- the impeller 53 consists of a hub 53a and a plurality of blades 53b.
- the hub 53a has a rotationally symmetrical shape about the axis AXL.
- One end side of the hub 53a is positioned on the inlet side of the supply air in the direction along the axis AXL, and the other end side of the hub 53a is positioned on the bearing housing 71 side.
- the outer peripheral surface of the hub 53a has a trumpet shape expanding from one end side to the other end side, and the hub 53a has a rear surface facing the bearing housing 71 (end wall 75) on the other end side.
- the impeller 53 consists of a hub 53a and a plurality of blades 53b.
- the hub 53a has a rotationally symmetrical shape about the axis AXL. In the direction along the axis AXL, one end side of the hub 53a is located on the inlet 51d side of the supply air, and the other end side of the hub 53a is located on the bearing housing 71 side.
- the outer peripheral surface of the hub 53a has a trumpet shape expanding from one end side to the other end side, and the hub 53a has a rear surface facing the bearing housing 71 (end wall 75) on the other end side.
- the hub 53a is provided with mounting holes 53a1 passing through the hub 53a along the axis AXL, and the mounting holes 53a1 are open at both ends of the hub 53a.
- the plurality of blades 53b are integrally attached to the outer peripheral surface of the hub 53a and arranged at predetermined intervals in the circumferential direction of the hub 53a.
- FIG. 2 is a longitudinal sectional view schematically showing the structure of the gas bearing device 10 shown in FIG. 1
- FIG. 3 is a transverse sectional view schematically showing the structure of the gas bearing device 10 shown in FIG. be.
- 4-1 is a front view of the snap rings 17 and 19 shown in FIG. 2
- FIG. 4-2 is a cross-sectional view (AA cross-sectional view) of the snap rings 17 and 19 shown in FIG. 4-1. ).
- the gas bearing device 10 is a bearing device that rotatably supports a rotating shaft 9 using gas as a working fluid. and a pair of snap rings 17, 19.
- a rotating shaft 9 passes through the housing 11 .
- the housing 11 is configured by the bearing portion 76 (78) described above, and the rotating shaft 9 is configured by the rotating shaft 91 described above.
- the top foil 13 is provided inside the housing 11 and has an annular shape surrounding the outer circumference of the rotating shaft 9 .
- the back spring 15 is provided between the top foil 13 and the housing 11 (shaft hole), and has a plurality of peaks 15a contacting the top foil 13 and a plurality of valleys 15b contacting the housing 11, respectively.
- a pair of snap rings 17 and 19 are fitted into a shaft hole through which the rotating shaft 9 of the housing 11 passes, and restrict movement of the back spring 15 in the axial direction of the rotating shaft 9 .
- the pair of snap rings 17 and 19 are snap rings for holes, and are fitted into ring grooves (circumferential grooves) provided in the shaft hole through which the rotating shaft 9 of the housing 11 passes. Fixed by elastic restoring force.
- the pair of snap rings 17 and 19 are annular with a part notched, and are formed so that the outer circumference and the inner circumference are concentrically aligned. Holes 17a and 19a for tools are provided in the portion.
- FIG. 5 is a view (cross-sectional view) showing an example in which turning grooves 17c, 19c inclined with respect to the axis AXL of the rotating shaft 9 are provided on the inner periphery of each of the pair of snap rings 17, 19, and
- FIG. 3 is a view (sectional view) showing an example in which turning grooves 9a1 and 9a2 inclined with respect to the axis AXL of the rotating shaft 9 are provided in the rotating shaft 9.
- the gas bearing device 10 has an inner circumference of at least one of the pair of snap rings 17 and 19 or at least one of the pair of snap rings 17 and 19 of the rotary shaft 9. , there are turning grooves 17c, 19c, 9a1, 9a2 inclined with respect to the axis AXL of the rotating shaft 9.
- each of the pair of snap rings 17 and 19 has swivel grooves 17c and 19c inclined with respect to the axis AXL of the rotating shaft 9 on the inner periphery thereof.
- the turning grooves 17c, 19c form spirals on the inner peripheries of the snap rings 17, 19 if air is introduced between the rotating shaft 9 and the top foil 13 by the rotation of the rotating shaft 9.
- the snap rings 17 and 19 may be formed with airfoils on their inner peripheries.
- turning grooves 9a1 and 9a2 inclined with respect to the axis line AXL of the rotating shaft 9 are provided in regions of the rotating shaft 9 facing the pair of snap rings 17 and 19, respectively.
- the turning grooves 9a1 and 9a2 may form a spiral on the outer circumference of the rotating shaft 9 as long as air is introduced between the rotating shaft 9 and the top foil 13 by the rotation of the rotating shaft 9.
- an airfoil may be formed on the outer circumference of the rotating shaft 9 .
- the turning grooves 17c, 19c of at least one of the pair of snap rings 17, 19 extend toward the area surrounded by the pair of snap rings 17, 19 in the direction opposite to the direction of rotation of the rotating shaft 9. inclined to According to such a configuration, when the rotating shaft 9 rotates, air is introduced between the rotating shaft 9 and the top foil 13 by the turning grooves 17c, 19c of at least one of the pair of snap rings 17, 19. be.
- the turning grooves 9 a 1 and 9 a 2 of the rotating shaft 9 are inclined in the same direction as the rotation direction of the rotating shaft 9 toward the region surrounded by the pair of snap rings 17 and 19 . According to such a configuration, air is introduced between the rotating shaft 9 and the top foil 13 by the turning grooves 9 a 1 and 9 a 2 of the rotating shaft 9 by rotating the rotating shaft 9 .
- Each of the pair of snap rings 17, 19 has a self-lubricating inner peripheral surface 17b, 19b.
- the inner peripheral surfaces 17b, 19b of the pair of snap rings 17, 19 have self-lubricating properties, so that the load of the rotating shaft 9 is absorbed only by the back spring 15 when the rotating shaft 9 rotates at a low speed. Since there is no need to support the back spring 15, the support rigidity of the back spring 15 can be reduced. As a result, a gas film can be reliably formed between the rotating shaft 9 and the top foil 13 when the rotating shaft 9 rotates at high speed. By reducing the support rigidity of the back spring 15, the pair of snap rings 17 and 19 support the rotary shaft 9 when the rotary shaft 9 rotates at low speed. Since the inner peripheral surfaces 17b, 19b have self-lubricating properties, one snap ring 17, 19 can reliably rotatably support the rotating shaft 9. As shown in FIG.
- Each of the pair of snap rings 17, 19 is made of a self-lubricating material. According to such a configuration, each of the pair of snap rings 17 and 19 is made of a self-lubricating material, so that the inner peripheral surfaces 17b and 19b of each of the pair of snap rings 17 and 19 are self-lubricating. have. Therefore, the supporting rigidity of the backup spring can be reduced.
- a self-lubricating material is a synthetic resin.
- the synthetic resin is a highly functional resin called engineering plastic (engineering plastic), and for example, MC nylon, polyacetal (POM), etc. can be used.
- engineering plastic engineing plastic
- MC nylon polyacetal
- POM polyacetal
- each of the pair of snap rings 17, 19 is made of synthetic resin.
- FIG. 7 is a view (sectional view) conceptually showing the relationship between the snap rings 17, 19 and the back spring 15, and FIG. 7-2 is a diagram showing the state of the rotating shaft 9 during low speed rotation, and FIG. 7-3 is a diagram showing the state of the rotating shaft 9 during medium speed rotation.
- FIG. 8 is a diagram for explaining the support rigidity of the back spring 15. As shown in FIG. Although the top foil 13 is omitted in FIG. 7, the top foil 13 is an essential component, and does not mean that the top foil 13 is not an essential component.
- the back spring 15 alone can rotate the rotating shaft as shown in FIG. 7-2. It is no longer necessary to support the load of 9, and the support rigidity of the back spring 15 can be reduced.
- the support rigidity of the back spring 15 is, as shown in FIG.
- the rotating shaft 9 when the rotating shaft 9 is installed, the rotating shaft 9 is supported by the back spring 15 and the snap rings 17, 19, and the height of the crest 15a of the back spring 15 is the same as that of the snap rings 17, 19. It is located at the same height as the inner circumference of 19. Even when the rotating shaft 9 rotates at a low speed, the peaks 15a of the back spring 15 are positioned at the same height as the inner circumferences of the snap rings 17 and 19, and the rotating shaft 9 is positioned between the back spring 15 and the snap rings 17 and 19. supported by As shown in FIG.
- a gas film can be reliably formed between the rotating shaft 9 and the top foil 13 when the rotating shaft 9 rotates at high speed.
- the pair of snap rings 17 and 19 support the rotary shaft 9 when the rotary shaft 9 rotates at low speed. Since the inner peripheral surfaces 17b, 19b have self-lubricating properties, the pair of snap rings 17, 19 can reliably rotatably support the rotating shaft 9. As shown in FIG.
- the present invention is not limited to the above-described embodiments, and includes modifications of the above-described embodiments and modes in which these modes are combined as appropriate.
- a gas bearing device (10) includes: A gas bearing device using gas as a working fluid, a rotating shaft (9); a housing (11) through which the rotating shaft (9) penetrates; An annular top foil (13) provided inside the housing (11) and surrounding the outer circumference of the rotating shaft (9); Provided between the top foil (13) and the housing (11), each of a plurality of peaks (15a) contacting the top foil (13) and valleys (15b) contacting the housing (11) is provided. a back spring (15); A pair of snap rings (17, 19) fitted into a shaft hole through which the rotating shaft (9) of the housing (11) passes to restrict the movement of the back spring (15) in the axial direction of the rotating shaft (9).
- a gas bearing device (10) according to another aspect is the gas bearing device (10) according to [1],
- the turning grooves (9a1, 9a2) of the rotating shaft (9) are inclined in the same direction as the rotating direction of the rotating shaft (9) toward the region surrounded by the pair of snap rings (17, 19). is doing.
- a gas bearing device (10) according to another aspect is the gas bearing device (10) according to [1] or [2],
- the turning grooves (17c, 19c) of at least one of the pair of snap rings (17, 19) extend toward the region surrounded by the pair of snap rings (17, 19). It is slanted in the direction opposite to the direction of rotation.
- a gas bearing device (10) according to another aspect is the gas bearing device (10) according to any one of [1] to [3],
- Each of the pair of snap rings (17, 19) has a self-lubricating inner peripheral surface (17b, 19b) for the rotating shaft (9).
- the inner peripheral surfaces (17b, 19b) of the pair of snap rings (17, 19) have self-lubricating properties, so that the back spring (15) can be lubricated when the rotating shaft (9) rotates at a low speed. It is no longer necessary to support the load of the rotating shaft (9) by itself, and the support rigidity of the back spring (15) can be reduced. As a result, a gas film can be reliably formed between the rotating shaft (9) and the top foil (13) when the rotating shaft (9) rotates at high speed.
- the pair of snap rings (17, 19) support the rotating shaft (9) when the rotating shaft (9) rotates at low speed. Since the inner peripheral surfaces (17b, 19b) of the snap rings (17, 19) have self-lubricating properties, the pair of snap rings (17, 19) reliably rotatably support the rotating shaft (9). be able to.
- a gas bearing device (10) according to another aspect is the gas bearing device (10) according to [4],
- Each of the pair of snap rings (17, 19) is made of a self-lubricating material.
- each of the pair of snap rings (17, 19) is made of a self-lubricating material, so that the inner peripheral surfaces (17b, 19b) of each of the pair of snap rings (17, 19) ) are self-lubricating. Therefore, the support rigidity of the back spring (15) can be reduced.
- a gas bearing device (10) according to another aspect is the gas bearing device (10) according to [5],
- the self-lubricating material is a synthetic resin.
- each of the pair of snap rings (17, 19) is made of synthetic resin.
- a turbocharger according to the aspect of [7], A gas bearing device (10) according to any one of [1] to [6] above is provided.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Supercharger (AREA)
- Support Of The Bearing (AREA)
- Mounting Of Bearings Or Others (AREA)
Abstract
Description
本願は、2021年2月26日に日本国特許庁に出願された特願2021-030501号に基づき優先権を主張し、その内容をここに援用する。
ガスを作動流体とするガス軸受装置であって、
回転軸と、
前記回転軸が貫通するハウジングと、
前記ハウジングの内部に設けられ、前記回転軸の外周を囲繞する、環状のトップフォイルと、
前記トップフォイルと前記ハウジングとの間に設けられ、前記トップフォイルに当接する山と前記ハウジングに当接する谷とが各々複数設けられたバックスプリングと、
前記ハウジングの前記回転軸が貫通する軸穴に嵌め込まれ、前記回転軸の軸方向において前記バックスプリングの移動を規制する一対のスナップリングと、
を備え、
前記一対のスナップリングの少なくとも一方、又は、前記回転軸の前記一対のスナップリングの少なくとも一方に対向する領域に、前記回転軸の軸線に対して傾斜した旋回溝を有する。
トップフォイル13は、ハウジング11の内部に設けられ、回転軸9の外周を囲繞する環状である。
バックスプリング15は、トップフォイル13とハウジング11(軸穴)との間に設けられ、トップフォイル13に当接する山15aとハウジング11に当接する谷15bとが各々複数設けられている。
このような構成によれば、回転軸9が回転することで、一対のスナップリング17,19の少なくとも一方が有する旋回溝17c,19cによって回転軸9とトップフォイル13との間に空気が導入される。
このような構成によれば、回転軸9が回転することで、回転軸9が有する旋回溝9a1,9a2によって回転軸9とトップフォイル13との間に空気が導入される。
このような構成によれば、一対のスナップリング17,19の各々の内周面17b,19bは自己潤滑性を有するので、回転軸9の低速回転時にバックスプリング15だけで回転軸9の荷重を支持する必要がなくなり、バックスプリング15の支持剛性を小さくすることができる。これにより、回転軸9の高速回転時に回転軸9とトップフォイル13との間にガス膜を確実に形成することができる。また、バックスプリング15の支持剛性を小さくすることで、回転軸9の低速回転時に一対のスナップリング17,19が回転軸9を支持することになるが、一対のスナップリング17,19の各々の内周面17b,19bが自己潤滑性を有することで、一つのスナップリング17,19が回転軸9を確実に回転可能に支持することができる。
このような構成によれば、一対のスナップリング17,19の各々は自己潤滑性材料で構成されているので、一対のスナップリング17,19の各々の内周面17b,19bは自己潤滑性を有する。よって、バックアップスプリングの支持剛性を小さくできる。
このような構成によれば、一対のスナップリング17,19の各々は合成樹脂で構成される。
ガスを作動流体とするガス軸受装置であって、
回転軸(9)と、
前記回転軸(9)が貫通するハウジング(11)と、
前記ハウジング(11)の内部に設けられ、前記回転軸(9)の外周を囲繞する、環状のトップフォイル(13)と、
前記トップフォイル(13)と前記ハウジング(11)との間に設けられ、前記トップフォイル(13)に当接する山(15a)と前記ハウジング(11)に当接する谷(15b)とが各々複数設けられたバックスプリング(15)と、
前記ハウジング(11)の前記回転軸(9)が貫通する軸穴に嵌め込まれ、前記回転軸(9)の軸方向において前記バックスプリング(15)の移動を規制する一対のスナップリング(17,19)と、
を備え、
前記一対のスナップリング(17,19)の少なくとも一方、又は、前記回転軸(9)の前記一対のスナップリング(17,19)の少なくとも一方に対向する領域に、前記回転軸(9)の軸線に対して傾斜した旋回溝(17c,19c,9a1,9a2)を有する。
前記回転軸(9)が有する前記旋回溝(9a1,9a2)は、前記一対のスナップリング(17,19)に囲まれた領域に向けて前記回転軸(9)の回転方向と同一方向に傾斜している。
前記一対のスナップリング(17,19)の少なくとも一方が有する前記旋回溝(17c,19c)は、前記一対のスナップリング(17,19)に囲まれた領域に向けて前記回転軸(9)の回転方向と反対方向に傾斜している。
前記一対のスナップリング(17,19)の各々は、前記回転軸(9)が自己潤滑性の内周面(17b,19b)を有する。
前記一対のスナップリング(17,19)の各々は、自己潤滑性材料で構成されている。
前記自己潤滑性材料は、合成樹脂である。
上記[1]から[6]のいずれか一つに記載のガス軸受装置(10)を備える。
3 タービン
31 タービンハウジング
31a 筒部(シュラウド部)
31b スクロール部
31c スロート部
31d 排気ガスの出口
33 タービン動翼(タービンインペラ)
33a ハブ
33a1 取付穴
33b 翼
5 コンプレッサ
51 コンプレッサハウジング
51a 筒部(シュラウド部)
51b スクロール部
51c ディフューザ部
51d 給気の入口
53 インペラ(コンプレッサインペラ)
53a ハブ
53a1 取付穴
53b 翼
71 軸受ハウジング
73 周壁(軸受ハウジング本体)
75 端壁(タービン側端壁)
751 シール部
76 軸受部
761 軸受穴
77 端壁(コンプレッサ側端壁)
771 蓋部材
773 シール部
78 軸受部
781 軸受穴
9 回転軸
9a1,9a2 旋回溝
91 回転軸
91a,91b 軸部
91c 中間部
91d タービン動翼取付部
91e コンプレッサインペラ取付部
10 ガス軸受装置
11 ハウジング
13 トップフォイル
15 バックスプリング
15a 山
15b 谷
17,19 スナップリング
17a,19a 工具用の穴
17b,19b 内周面
17c,19c 旋回溝
AXL 軸線
Claims (7)
- ガスを作動流体とするガス軸受装置であって、
回転軸と、
前記回転軸が貫通するハウジングと、
前記ハウジングの内部に設けられ、前記回転軸の外周を囲繞する、環状のトップフォイルと、
前記トップフォイルと前記ハウジングとの間に設けられ、前記トップフォイルに当接する山と前記ハウジングに当接する谷とが各々複数設けられたバックスプリングと、
前記ハウジングの前記回転軸が貫通する軸穴に嵌め込まれ、前記回転軸の軸方向において前記バックスプリングの移動を規制する一対のスナップリングと、
を備え、
前記一対のスナップリングの少なくとも一方、又は、前記回転軸の前記一対のスナップリングの少なくとも一方に対向する領域に、前記回転軸の軸線に対して傾斜した旋回溝を有する、ガス軸受装置。 - 前記回転軸が有する前記旋回溝は、前記一対のスナップリングに囲まれた領域に向けて前記回転軸の回転方向と同一方向に傾斜している、
請求項1に記載のガス軸受装置。 - 前記一対のスナップリングの少なくとも一方が有する前記旋回溝は、前記一対のスナップリングに囲まれた領域に向けて前記回転軸の回転方向と反対方向に傾斜している、
請求項1又は2に記載のガス軸受装置。 - 前記一対のスナップリングの各々は、前記回転軸が自己潤滑性の内周面を有する、請求項1から3のいずれか一項に記載のガス軸受装置。
- 前記一対のスナップリングの各々は、自己潤滑性材料で構成されている、請求項4に記載のガス軸受装置。
- 前記自己潤滑性材料は、合成樹脂である、請求項5に記載のガス軸受装置。
- 請求項1から6のいずれか一項に記載のガス軸受装置を備えるターボチャージャ。
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Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS63166719U (ja) * | 1987-04-20 | 1988-10-31 | ||
JPH07293559A (ja) * | 1994-04-19 | 1995-11-07 | Nippon Seiko Kk | すべり軸受 |
JP2004092771A (ja) * | 2002-08-30 | 2004-03-25 | Shimadzu Corp | フォイル型動圧ガス軸受 |
KR100938919B1 (ko) * | 2007-08-22 | 2010-01-28 | 한국기계연구원 | 그루브가 형성된 포일 베어링 |
US20150362012A1 (en) * | 2012-11-02 | 2015-12-17 | Yury Ivanovich Ermilov | Foil bearing assembly |
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JP7257156B2 (ja) | 2019-01-31 | 2023-04-13 | 三菱重工業株式会社 | ガス軸受及び回転機械 |
JP2021030501A (ja) | 2019-08-20 | 2021-03-01 | 三菱ケミカル株式会社 | ストレッチ包装用フィルム |
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- 2022-02-21 DE DE112022000416.9T patent/DE112022000416T5/de active Pending
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Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS63166719U (ja) * | 1987-04-20 | 1988-10-31 | ||
JPH07293559A (ja) * | 1994-04-19 | 1995-11-07 | Nippon Seiko Kk | すべり軸受 |
JP2004092771A (ja) * | 2002-08-30 | 2004-03-25 | Shimadzu Corp | フォイル型動圧ガス軸受 |
KR100938919B1 (ko) * | 2007-08-22 | 2010-01-28 | 한국기계연구원 | 그루브가 형성된 포일 베어링 |
US20150362012A1 (en) * | 2012-11-02 | 2015-12-17 | Yury Ivanovich Ermilov | Foil bearing assembly |
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US20240141952A1 (en) | 2024-05-02 |
JP2022131521A (ja) | 2022-09-07 |
CN116897252A (zh) | 2023-10-17 |
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