WO2015001927A1 - アクチュエータの動力伝達機構および過給機 - Google Patents
アクチュエータの動力伝達機構および過給機 Download PDFInfo
- Publication number
- WO2015001927A1 WO2015001927A1 PCT/JP2014/065441 JP2014065441W WO2015001927A1 WO 2015001927 A1 WO2015001927 A1 WO 2015001927A1 JP 2014065441 W JP2014065441 W JP 2014065441W WO 2015001927 A1 WO2015001927 A1 WO 2015001927A1
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- WIPO (PCT)
- Prior art keywords
- bearing
- drive shaft
- power transmission
- transmission mechanism
- actuator
- Prior art date
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Classifications
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- 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
- F02B37/24—Control of the pumps by using pumps or turbines with adjustable guide vanes
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- 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
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
- F01D17/16—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
- F01D17/165—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes for radial flow, i.e. the vanes turning around axes which are essentially parallel to the rotor centre line
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- 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 power transmission mechanism of an actuator and a supercharger that adjust an inclination angle with respect to a fluid flow direction.
- variable capacity turbines have been adopted for turbochargers and the like.
- a plurality of nozzle vanes arranged in an annular arrangement in a flow path for guiding exhaust gas from a scroll flow path on the turbine side to a turbine impeller are fixed to the shaft (blade shaft).
- This shaft is rotatably supported by a shaft hole formed in the flow path wall surface.
- a nozzle vane changes an angle in a flow path with rotation of a shaft, a flow path area will change and the flow volume of the fluid which distribute
- the above shaft is rotated by the power of the actuator.
- a power transmission mechanism is disposed between the actuator and the shaft, and the power of the actuator is converted into a force in a direction for rotating the shaft through the power transmission mechanism.
- the actuator is provided outside the housing of the turbocharger, and in order to transmit power to the shaft located inside the housing, the power transmission mechanism is supported by a bearing press-fitted into a through-hole penetrating the housing, and the bearing. Drive shaft.
- an object of the present invention is to provide an actuator power transmission mechanism and a supercharger with improved durability.
- a first aspect of the present invention is a power transmission mechanism of an actuator, the rotating plate rotating by the power of the actuator, a driving shaft fixed to the rotating plate and rotating integrally with the rotating plate, and the other end of the driving shaft.
- One or a plurality of adjusting portions that are directly or indirectly connected to the side, rotate in conjunction with the drive shaft, and adjust the inclination angle with respect to the fluid flow direction, and an insertion hole through which the drive shaft is inserted
- a bearing that rotatably supports the drive shaft, and an outer peripheral surface of the bearing is provided with a deterrent section that suppresses water from entering the insertion hole that has traveled along the outer peripheral surface of the bearing. Is formed into a cylindrical shape that is press-fitted into the housing, and the outer peripheral surface of the bearing is exposed between the housing and the rotating plate.
- the restraining portion may be configured by a bearing protrusion that protrudes in the radial direction of the drive shaft from the outer peripheral surface of the bearing.
- the bearing protrusion may extend annularly over the circumferential direction of the drive shaft.
- a groove extending in the circumferential direction of the bearing may be formed on the outer peripheral surface of the bearing, and the bearing protrusion may be fitted into the groove.
- the rotary plate may be provided with a rotary plate protrusion that protrudes toward the other end side of the drive shaft and is located on the radially outer side of the drive shaft.
- the bearing protrusion and the rotating plate protrusion may overlap at least partially when viewed from the radial direction of the drive shaft.
- the bearing protrusion may include a cylindrical portion that contacts the outer peripheral surface of the bearing, and a plate portion that is connected to the cylindrical portion and is formed in a disk shape through which the bearing passes.
- the bearing protrusion may further include a cylindrical portion having an outer diameter and an inner diameter larger than those of the cylindrical portion.
- the said board part is provided between these cylinder parts, and connects these cylinder parts.
- a second aspect of the present invention is a supercharger provided with the power transmission mechanism of the actuator described above.
- FIG. 1 is a schematic cross-sectional view of a supercharger according to an embodiment of the present invention.
- FIG. 2 is a plan view of the drive ring as viewed from the left side of FIG.
- FIG. 3 is a plan view of the drive ring and the connecting portion viewed from the right side of FIG.
- FIG. 4 is an explanatory diagram for explaining the power transmission mechanism.
- FIG. 5A and FIG. 5B are external views of the supercharger.
- FIG. 6A to FIG. 6D are explanatory views for explaining a power transmission mechanism as a modification of the present embodiment.
- a waste gate valve (adjusting unit) that adjusts an inflow amount (outflow amount) of exhaust gas to a bypass passage that bypasses the turbine impeller
- a supercharger including a valve (adjusting unit) that adjusts an inflow amount (outflow amount) of a fluid into a bypass flow path that bypasses the compressor impeller is conceivable.
- a supercharger that opens and closes a valve (adjustment unit) that adjusts the flow rate of exhaust gas flowing into the upstream and downstream turbochargers with an actuator.
- a valve adjustment unit
- the present invention is not limited to a supercharger, and can also be applied as a power transmission mechanism that transmits the power of an actuator mounted on another device.
- a protrusion 2 a is provided on the outer peripheral surface of the bearing housing 2 in the vicinity of the turbine housing 4.
- the protrusion 2 a protrudes in the radial direction of the bearing housing 2.
- a projection 4 a is provided on the outer peripheral surface of the turbine housing 4 in the vicinity of the bearing housing 2.
- the protrusion 4 a protrudes in the radial direction of the turbine housing 4.
- the bearing housing 2 and the turbine housing 4 are fixed by fastening the protrusions 2 a and 4 a with the fastening mechanism 3.
- the fastening mechanism 3 includes a coupling (so-called G coupling) that holds the protrusions 2a and 4a.
- a hole (bearing hole) 2b penetrating in the left-right direction of the supercharger C is formed in the bearing housing 2.
- the turbine shaft 7 is inserted into the hole 2b and is rotatably supported through a bearing.
- a turbine impeller 8 is integrally connected to one end of the turbine shaft 7.
- the turbine impeller 8 is rotatably accommodated in the turbine housing 4.
- a compressor impeller 9 is integrally connected to the other end of the turbine shaft 7.
- the compressor impeller 9 is rotatably accommodated in the compressor housing 6.
- a discharge port 14 is formed in the turbine housing 4.
- the discharge port 14 communicates with the turbine scroll passage 13 via the turbine impeller 8.
- the discharge port 14 faces the front surface of the turbine impeller 8 and is connected to an exhaust gas purification device (not shown).
- the turbine scroll passage 13 communicates with a gas inlet (not shown) through which exhaust gas discharged from the engine is guided. Further, the turbine scroll flow path 13 communicates with the variable flow path x. Accordingly, the exhaust gas is guided from the gas inlet to the turbine scroll passage 13 and then to the discharge port 14 via the variable passage x and the turbine impeller 8. In this circulation process, the exhaust gas rotates the turbine impeller 8. The rotational force of the turbine impeller 8 is transmitted to the compressor impeller 9 via the turbine shaft 7. The fluid is pressurized by the transmitted rotational force of the compressor impeller 9 and guided to the intake port of the engine.
- variable flow passage x of the turbine housing 4 is provided with a variable stationary blade mechanism 20 that adjusts the communication opening degree between the turbine scroll flow passage 13 and the discharge port 14.
- the variable stationary blade mechanism 20 changes the flow rate of the exhaust gas guided to the turbine impeller 8 according to the flow rate of the exhaust gas. Specifically, the variable stationary blade mechanism 20 reduces the flow rate of the exhaust gas guided to the turbine impeller 8 by reducing the opening of the variable flow path x when the engine speed is low and the flow rate of the exhaust gas is small. Improve. Thereby, the turbine impeller 8 can be rotated even with a small flow rate. Below, the structure of the variable stationary blade mechanism 20 is demonstrated.
- the variable stationary blade mechanism 20 includes a shroud plate 21 that forms the left wall surface of the variable flow path x and a counter plate 22 that forms the right wall surface of the variable flow path x.
- the shroud plate 21 and the counter plate 22 are annular members, respectively, and are opposed to each other in the axial direction of the turbine shaft 7. That is, the axial clearance between the shroud plate 21 and the opposing plate 22 in the turbine shaft 7 constitutes the variable flow path x.
- shroud plate 21 has an annular cylindrical portion 21b extending from the flange portion facing the opposing plate 22 toward the discharge port 14. A portion that continues from the flange portion to the cylindrical portion 21 b is formed as a shroud wall that faces the radially outer side of the turbine impeller 8.
- the nozzle vane 23 (adjustment unit) is a member whose axial length in the turbine shaft 7 is slightly smaller than the interval of the variable flow path x in the axial direction in the turbine shaft 7, and includes two shafts (blade shafts) 23a, 23b.
- the shafts 23a and 23b are rotatably supported in the hole 21a of the shroud plate 21 and the hole 22a of the counter plate 22, respectively.
- a plurality of nozzle vanes 23 are arranged in the variable flow path x, one for each hole 21a (hole 22a).
- FIG. 2 is a plan view of the drive ring 24 as viewed from the left side of FIG.
- the drive ring 24 has an annular flange portion 24b having an outer diameter larger than that of the cylindrical portion 24a.
- the flange portion 24b extends radially outward from the end of the cylindrical portion 24a, and a plurality of holes (ring holes) 24c are formed at equal intervals in the circumferential direction.
- a protrusion 24d protruding in the radial direction of the drive ring 24 is formed on the upper side of the drive ring 24 in FIG.
- a hole (ring hole) 24 e penetrating in the axial direction of the turbine shaft 7 is formed in the protruding portion 24 d.
- FIG. 3 is a plan view of the drive ring 24 and the connecting portion 25 as viewed from the right side of FIG.
- the connecting portion 25 is a so-called U-shaped (Y-shaped) member having two arms.
- a hole (connection hole) 25 a penetrating in the axial direction of the turbine shaft 7 is formed in the connection portion 25.
- One end of a shaft 23a is inserted into the hole 25a from the right side and fixed.
- the connecting portion 25 is arranged so that one end side where the hole 25a is formed faces inward in the radial direction of the cylindrical portion 24a of the drive ring 24.
- a connecting pin 26 (see FIG. 1) is located in a gap 25b between both portions (arms) branched into two forks on the other end side of the connecting portion 25. One end of the connecting pin 26 is inserted through the hole 24c.
- one end of a protruding pin 27 is inserted into the hole 24e of the drive ring 24 from the right side.
- An interlocking plate 28 is disposed on the right side of the protrusion 24 d of the drive ring 24.
- the interlocking plate 28 is inserted with the other end of the drive shaft 30 constituting the power transmission mechanism 29 and rotates integrally with the drive shaft 30.
- the interlocking plate 28 has a notch formed on the lower side in FIG.
- the protruding pin 27 is positioned in the gap 28b in the notch.
- the drive ring 24 to which the protruding pin 27 is fixed is swung.
- the cylindrical portion 24 a of the drive ring 24 is inserted through the hole 21 a of the shroud plate 21. Therefore, the drive ring 24 rotates in the circumferential direction of the cylindrical portion 24a.
- the nozzle vane 23 rotates around the shaft 23 a via the connecting portion 25.
- FIG. 4 is an explanatory diagram for explaining the power transmission mechanism 29, and is an extraction diagram of a broken line portion of FIG.
- the power transmission mechanism 29 has a first lever 31 (rotary plate) to which the other end of the drive shaft 30 is fixed.
- the first lever 31 has a lever hole 31 a penetrating in the axial direction of the drive shaft 30 on one end side, and a drive hole 31 b penetrating in the axial direction of the drive shaft 30 on the other end side.
- One end of the drive shaft 30 is inserted into the drive hole 31 b from the left side, welded from the right side and closed, and one end of the drive shaft 30 is fixed to the first lever 31. That is, the first lever 31 rotates integrally with the drive shaft 30.
- FIG. 5 is an external view of the supercharger C
- FIG. 5A shows a front view of the supercharger C
- FIG. 5B shows a right side view of the supercharger C.
- the supercharger C is provided with an actuator 32 outside the housing.
- the actuator 32 is composed of a motor or the like, and rotates a fixed shaft 34 fixed to one end of the second lever 33 shown in FIG. 5B in accordance with control of a control unit (not shown).
- One end of a rod 36 is rotatably connected to the other end of the second lever 33 via a movable shaft 35.
- the other end of the rod 36 and the first lever 31 are rotatably connected via a movable shaft 37.
- the movable shaft 37 is inserted through the lever hole 31a.
- the power of the actuator 32 is transmitted to the first lever 31 via the second lever 33, the fixed shaft 34, the movable shaft 35, the rod 36, and the movable shaft 37, and the first lever 31 is centered on the drive shaft 30. Rotate to. Since the first lever 31 is fixed to one end of the drive shaft 30, when the first lever 31 is rotated by the power of the actuator 32, the drive shaft 30 is also rotated. As a result, as described above, the nozzle vane 23 changes the angle in the variable flow path x as the shaft 23a rotates.
- the nozzle vane 23 is indirectly connected to the other end side of the drive shaft 30 and rotates in conjunction with the drive shaft 30 to change the inclination angle with respect to the fluid flow direction.
- the area of the variable flow path x changes.
- the bearing 38 is formed in a cylindrical shape having a longitudinal direction.
- the bearing 38 has an insertion hole 38a extending in the longitudinal direction.
- the drive shaft 30 is inserted through the insertion hole 38a, and the bearing 38 rotatably supports the drive shaft 30.
- a hole (housing hole) 4 b is formed in the turbine housing 4.
- the hole 4 b passes through the turbine housing 4 in the axial direction of the turbine shaft 7.
- a part of the bearing 38 is press-fitted into the hole 4 b and fixed, and the remaining part is exposed to the outside from the turbine housing 4. That is, an outer peripheral surface (described later) 38 b of the bearing 38 is exposed between the turbine housing 4 and the first lever 31.
- the outer peripheral surface 38 b of the bearing 38 is provided with a restraining portion 39 that suppresses water from entering the insertion hole 38 a that has passed through the outer peripheral surface 38 b of the bearing 38.
- the restraining portion 39 is configured by a bearing protrusion 39 a that protrudes from the outer peripheral surface 38 b of the bearing 38 in the radial direction of the drive shaft 30.
- An annular groove 38 c is formed on the outer peripheral surface 38 b of the bearing 38.
- the groove 38 c is recessed radially inward of the bearing 38. Further, the groove 38 c extends in the circumferential direction of the bearing 38.
- the bearing protrusion 39 a is configured by an annular member that extends in an annular shape over the circumferential direction of the drive shaft 30.
- the bearing protrusion 39a is fitted in the groove 38c.
- the inner diameter of the bearing protrusion 39a is larger than the outer diameter of the groove 38c.
- the outer diameter of the bearing protrusion 39 a is larger than the outer diameter of the bearing 38.
- a notch is partly formed in the bearing protruding portion 39a so as to facilitate attachment to the groove 38c.
- the inhibiting unit 39 inhibits the water from traveling to the right side in FIG. 4 through the bearing 38 from the turbine housing 4. Further, the suppression unit 39 suppresses the intrusion of water from the gap between the bearing 38 and the first lever 31 into the insertion hole 38 a of the bearing 38 and the gap between the drive shaft 30. Therefore, generation
- the restraining portion 39 is constituted by the bearing protruding portion 39a that protrudes in the radial direction of the drive shaft 30 from the outer peripheral surface 38b of the bearing 38, the structure is simple and the design is easy.
- the bearing protrusion 39a extends in an annular shape over the circumferential direction of the drive shaft 30, no matter what position in the circumferential direction of the outer peripheral surface 38b of the bearing 38 the water is transmitted, the bearing protrusion 39a Can be prevented. Further, the water transmitted along the outer peripheral surface 38b of the bearing 38 is guided vertically downward along the groove 38c along the groove bottom of the groove 38c. As described above, the groove 38c can also prevent the water from proceeding to the gap between the insertion hole 38a of the bearing 38 and the drive shaft 30.
- bearing protrusion 39a is an annular member that fits into the groove 38c, the processing of the bearing 38 becomes easier as compared with the case where the outer peripheral surface 38b of the bearing 38 is cut out to form the bearing protrusion.
- FIG. 6 is an explanatory diagram for explaining power transmission mechanisms 29a to 29d as modifications of the present embodiment.
- the power transmission mechanism 29a of the first modified example shown in FIG. 6A has a restraining portion 49 composed of a bearing protrusion 49a.
- the bearing protrusion 49a is an annular member, and is continuously formed from the small diameter portion 49b to the first lever 31 side through a small diameter portion (tubular portion) 49b through which the bearing 38 is inserted and comes into contact with the outer peripheral surface 38b of the bearing 38.
- the large-diameter portion (cylinder portion) 49c has a larger outer diameter and inner diameter than the small-diameter portion 49b.
- the small diameter part (cylinder part) 49b and the large diameter part (cylinder part) 49c are connected to each other by the plate part (connection part) 49d provided therebetween.
- the plate portion 49d is formed in a disk shape through which the bearing 38 passes.
- the plate portion 49d is connected to the small diameter portion 49b at the inner end in the radial direction.
- the plate portion 49d is connected to the large-diameter portion 49c at the outer end in the radial direction.
- the inner diameter of the large diameter portion 49c is larger than the outer diameter of the rotating plate protrusion 31d of the first lever 31.
- the distal end side of the rotating plate protruding portion 31d is located on the radially inner side of the large-diameter portion 49c. That is, the bearing protrusion 49 a and the rotating plate protrusion 31 d are at least partially overlapped when viewed from the radial direction of the drive shaft 30. Note that the overlapping portions of the bearing protrusion 49a and the rotating plate protrusion 31d may be separated from each other at a predetermined interval in the radial direction of the drive shaft 30 or may be in contact with each other.
- the large diameter portion 49c of the bearing protrusion 49a is located on the radially outer side of the rotating plate protrusion 31d.
- the rotating plate protrusion 31d may be located on the radially outer side of the large diameter portion 49c of the bearing protrusion 49a. In this case, even if the water reaches the leading end portion in the protruding direction of the rotating plate protruding portion 31d, the large diameter portion 49c of the bearing protruding portion 49a can prevent the water from proceeding into the bearing 38.
- the large-diameter portion 49c may be omitted according to the structure of the first lever 31 (for example, when the rotating plate protruding portion 31d is omitted), the usage environment of the power transmission mechanism 29a, and the like.
- the restraining part 49 has only a small diameter part 49b and a plate part 49d connected to one end of the small diameter part 49b.
- the power transmission mechanism 29b of the second modified example shown in FIG. 6B has a restraining portion 59 composed of a bearing protruding portion 59a.
- the bearing protrusion 59 a is stainless wool or glass wool wound around the outer peripheral surface 38 b of the bearing 38.
- the bearing protrusion 59a can prevent water from entering the bearing 38 by filling a gap between the rotating plate protrusion 31d and the outer peripheral surface 38b of the bearing 38 or by narrowing the gap.
- the power transmission mechanism 29c of the third modified example shown in FIG. 6C has a restraining portion 69 configured by a bearing protrusion 69a.
- the bearing protrusion 69a is formed of an annular member that fits into the groove 38c, as in the above-described embodiment, but an inclined surface 69b is formed on the first lever 31 side.
- the inclined surface 69b is a surface whose outer diameter increases as the distance from the first lever 31 side increases in the axial direction of the drive shaft 30, and the inclined surface 69b is located on the radially inner side of the rotating plate protrusion 31d. ing.
- the adjustment unit (nozzle vane 23) is indirectly connected to the drive shaft 30 via a plurality of members.
- the adjustment unit is connected to the drive shaft 30. And may be directly connected.
- the power transmission mechanisms 29, 29a to 29d of the actuator 32 may be applied to the power transmission mechanism of the actuator that adjusts the opening degree of the wastegate valve of the supercharger.
- the power transmission mechanisms 29, 29a to 29d of the actuator 32 are exhausted to both scroll channels. You may apply to the power transmission mechanism of the actuator which adjusts the opening degree of the valve which adjusts the inflow ratio of gas.
- valve body of the valve corresponds to the adjustment unit (nozzle vane 23) described above.
- a bearing that is press-fitted into a through hole provided in the turbine housing corresponds to the bearing 38 described above.
- the stem supported by the bearing corresponds to the drive shaft 30 described above.
- the link plate connected to the end of the stem protruding outside the turbine housing and rotated by the power of the actuator corresponds to the above-described rotation plate (first lever 31).
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Supercharger (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
- Control Of Turbines (AREA)
Abstract
Description
Claims (9)
- アクチュエータの動力で回転する回転板と、
一端が前記回転板に固定され、該回転板と一体回転する駆動軸と、
前記駆動軸の他端側に直接、または、間接的に連結され、該駆動軸と連動して回転し、流体の流れ方向に対する傾斜角度を調整する1または複数の調整部と、
前記駆動軸が挿通される挿通孔を有し、該駆動軸を回転自在に支持する軸受と、
を備え、
前記軸受の外周面には、該軸受の外周面を伝った前記挿通孔への水の浸入を抑える抑止部が設けられ、
前記軸受はその一部がハウジングに圧入される筒状に形成され、
前記軸受の前記外周面は、前記ハウジングと前記回転板の間で露出していることを特徴とするアクチュエータの動力伝達機構。 - 前記抑止部は、前記軸受の外周面から前記駆動軸の径方向に突出する軸受突出部で構成されることを特徴とする請求項1に記載のアクチュエータの動力伝達機構。
- 前記軸受突出部は、前記駆動軸の周方向に亘って環状に延在することを特徴とする請求項2に記載のアクチュエータの動力伝達機構。
- 前記軸受の外周面には該軸受の周方向に延在する溝が形成され、
前記軸受突出部は、前記溝に嵌合することを特徴とする請求項3に記載のアクチュエータの動力伝達機構。 - 前記回転板には、前記駆動軸の他端側に向かって突出し、該駆動軸の径方向外側に位置する回転板突出部が設けられていることを特徴とする請求項1から4のいずれか1項に記載のアクチュエータの動力伝達機構。
- 前記軸受突出部と、前記回転板突出部とは、前記駆動軸の径方向から見て少なくとも一部が重なることを特徴とする請求項5に記載のアクチュエータの動力伝達機構。
- 前記軸受突出部は、
前記軸受の前記外周面と当接する筒部と、
前記筒部に接続し、前記軸受が貫通する円盤状に形成される板部と
を有することを特徴とする請求項2に記載のアクチュエータの動力伝達機構。 - 前記軸受突出部は、さらに、
前記筒部よりも外径及び内径が大きい筒部を有し、
前記板部はこれらの筒部の間に設けられ、これらの筒部を連結することを特徴とする請求項7に記載のアクチュエータの動力伝達機構。 - 請求項1から8のいずれか1項に記載のアクチュエータの動力伝達機構を備えた過給機。
Priority Applications (4)
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JP2015525119A JP6056973B2 (ja) | 2013-07-04 | 2014-06-11 | アクチュエータの動力伝達機構および過給機 |
CN201480033070.5A CN105283647B (zh) | 2013-07-04 | 2014-06-11 | 致动器的动力传递机构以及增压器 |
KR1020157028011A KR101958897B1 (ko) | 2013-07-04 | 2014-06-11 | 액추에이터 동력 전달 기구 및 터보차저 |
US14/857,154 US10107186B2 (en) | 2013-07-04 | 2015-09-17 | Actuator power transmission mechanism and turbocharger |
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JP2013141002 | 2013-07-04 | ||
JP2013-141002 | 2013-07-04 |
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US14/857,154 Continuation US10107186B2 (en) | 2013-07-04 | 2015-09-17 | Actuator power transmission mechanism and turbocharger |
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WO2015001927A1 true WO2015001927A1 (ja) | 2015-01-08 |
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US (1) | US10107186B2 (ja) |
JP (1) | JP6056973B2 (ja) |
KR (1) | KR101958897B1 (ja) |
CN (1) | CN105283647B (ja) |
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WO2016095940A1 (en) * | 2014-12-19 | 2016-06-23 | Volvo Truck Corporation | A turbocharger, and a method for manufacturing a turbocharger |
US9964010B2 (en) * | 2016-05-11 | 2018-05-08 | GM Global Technology Operations LLC | Turbocharger actuation shaft exhaust leakage containment method |
CN112096514B (zh) * | 2016-08-24 | 2022-05-31 | 株式会社Ihi | 可变容量型增压器 |
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JP2005113797A (ja) * | 2003-10-08 | 2005-04-28 | Aisin Seiki Co Ltd | ターボチャージャの排気ガスシール構造 |
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- 2014-06-11 WO PCT/JP2014/065441 patent/WO2015001927A1/ja active Application Filing
- 2014-06-11 KR KR1020157028011A patent/KR101958897B1/ko active IP Right Grant
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2015
- 2015-09-17 US US14/857,154 patent/US10107186B2/en active Active
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Also Published As
Publication number | Publication date |
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US10107186B2 (en) | 2018-10-23 |
CN105283647A (zh) | 2016-01-27 |
CN105283647B (zh) | 2017-11-21 |
KR20150122251A (ko) | 2015-10-30 |
JP6056973B2 (ja) | 2017-01-11 |
KR101958897B1 (ko) | 2019-03-15 |
US20160003138A1 (en) | 2016-01-07 |
JPWO2015001927A1 (ja) | 2017-02-23 |
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