WO2013061357A1 - ターボ用アクチュエータ - Google Patents
ターボ用アクチュエータ Download PDFInfo
- Publication number
- WO2013061357A1 WO2013061357A1 PCT/JP2011/005933 JP2011005933W WO2013061357A1 WO 2013061357 A1 WO2013061357 A1 WO 2013061357A1 JP 2011005933 W JP2011005933 W JP 2011005933W WO 2013061357 A1 WO2013061357 A1 WO 2013061357A1
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- WO
- WIPO (PCT)
- Prior art keywords
- shaft
- housing
- rotor
- seal member
- turbo
- 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
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
- F02B37/183—Arrangements of bypass valves or actuators therefor
- F02B37/186—Arrangements of actuators or linkage for bypass valves
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- 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
- F16H—GEARING
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
- F16H25/20—Screw mechanisms
- F16H25/24—Elements essential to such mechanisms, e.g. screws, nuts
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- 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
- F16H—GEARING
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
- F16H25/20—Screw mechanisms
- F16H2025/2062—Arrangements for driving the actuator
- F16H2025/2075—Coaxial drive motors
- F16H2025/2078—Coaxial drive motors the rotor being integrated with the nut or screw body
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- 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
- F16H—GEARING
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
- F16H25/20—Screw mechanisms
- F16H25/24—Elements essential to such mechanisms, e.g. screws, nuts
- F16H2025/2436—Intermediate screw supports for reducing unsupported length of screw shaft
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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 turbo actuator for driving a lever for opening and closing a waste gate valve of a turbocharger, a lever for opening and closing a nozzle vane of a VG (Variable Geometry) turbo, and the like.
- a turbocharger which is attracting attention as a means of improving fuel consumption by downsizing the engine.
- a turbocharger is configured to rotate a turbine with exhaust gas from an engine, drive a compressor coaxial with the turbine to compress intake air, and supply the compressed air to the engine. Since the mass flow rate of compressed air is the same even if the volumetric flow rate is the same, the displacement can be reduced without reducing the engine output. Therefore, when the engine can be downsized and power is required (on a slope or at high speed), the turbocharger is used.
- Such a turbocharger as a means for realizing downsizing of the engine needs to control the supercharging pressure more precisely than a turbocharger for conventional use. Therefore, there is a tendency to use an electrically driven actuator capable of controlling the valve opening with high accuracy as a turbo actuator for controlling the supercharging pressure (see, for example, Patent Document 1).
- the bush 102 fitted into the end portion of the housing 100 supports the columnar shaft 101 so as to be slidable in the linear motion direction X.
- the exhaust gas flows from the engine upstream of the exhaust turbine to the exhaust passage 110 and is introduced into the exhaust turbine. However, a part of the exhaust gas is released to the downstream side of the exhaust turbine to control the boost pressure.
- a wastegate 111 is opened in the exhaust passage 110. The exhaust gas flowing from the waste gate 111 to the exhaust bypass passage 108 bypasses the exhaust turbine and is introduced downstream.
- the lever 105 is rotated about the fulcrum 107 by the linear movement of the shaft 101, whereby the waste gate valve 109 is rotated to open and close the waste gate 111 to control the supercharging pressure.
- the conventional turbo actuator is configured as described above, when the lever 105 rotates, the position on the rotating tip side is displaced by a displacement amount D (shown in FIG. 5), and the rod 104 and the shaft 101 are moved. Swings in the swing direction Y. Therefore, there is a problem that the bush 102 is pressed by the swing of the shaft 101 to cause deformation and rattling, and the seal member 103 is pressed to the bush 102 and the sealing performance is biased.
- Patent Document 1 if the linear expansion coefficients of the housing 100 and the bush 102 are different, there is a problem that a gap is generated between the housing 100 and the bush 102 when the temperature of the engine becomes high due to the heat of the engine. Furthermore, in the above-mentioned patent document 1, since the shoulder portion whose diameter of the shaft 101 is enlarged is caused to collide with the bushing 102, the direct movement of the shaft 101 during abnormal operation is restricted. In some cases, the seal member 103 deforms the seal member 102 and impairs the sealing performance. Further, the bush 102 and the seal member 103 may come out of the housing 100 due to a collision force.
- the present invention has been made to solve the above-described problems, and is used for a turbo that slidably supports without losing the sealing performance while suppressing the swing of the shaft accompanying the rotation of the turbo lever.
- An object is to provide an actuator.
- the turbo actuator according to the present invention includes a stator, a rotor that is rotatably arranged inside the stator, and has a female screw portion formed in a hole provided in the center, and a female screw portion that is screwed into one end portion.
- a seal member that is inserted into the shaft housing and closes the gap between the shaft housing and the cylindrical portion of the shaft, and is fixed to the shaft housing and sandwiches the seal member between the first sliding support portion and
- a second sliding support unit for slidably supporting the cylindrical portion In which and a second sliding support unit for slidably supporting the cylindrical portion.
- the two slide support portions that slidably support the cylindrical portion of the shaft are provided so as to receive the load of the shaft, the swing of the shaft accompanying the rotation of the turbo side lever is suppressed. can do.
- the first sliding support portion is formed integrally with the shaft housing, deformation and rattling can be prevented, and further, deformation of the seal member adjacent to the first sliding support portion can be prevented. Therefore, the shaft can be slidably supported without impairing the sealing performance.
- FIGS. 3A and 3B are cross-sectional views showing a configuration of a shaft and a shaft housing.
- FIG. 3A is a view taken along arrows II
- FIG. 3B is a view taken along arrows II-II
- FIG. 3A is a view taken along arrows II
- FIG. 3B is a view taken along arrows II-II
- the turbo actuator 1 shown in FIG. 1 mainly includes a shaft 2 that drives a lever 105 on the turbocharger side, and a motor unit 3 that linearly moves the shaft 2 in the linear motion direction X.
- a rod 104 is attached to the distal end side of the shaft 2, and a lever 105 is attached to the distal end of the rod 104 so as to be bendable.
- the wastegate valve 109 (shown in FIG. Control valve opening.
- a motor with a brush is used in the example of FIG.
- a stator 4 and a coil 5 wound around the stator 4 are provided and fixed to the motor housing 6 by molding.
- the motor housing 6 is also provided with a brush 7 for supplying power to the coil 5, a power supply terminal 8 for supplying power to the brush 7, a position sensor 9 for detecting the position of the shaft 2, and the like.
- a rotor 10 Inside the stator 4, a rotor 10, an NS magnetized magnet 11 attached to the rotor 10, and a commutator 12 that energizes the coil 5 by sliding against the brush 7 rotate. It is provided as possible.
- the rotor 10 and the magnet 11 are rotatably supported by a bearing 13, and a female screw portion 10 a is formed in a hole provided in the center of the rotor 10.
- FIG. 2 is an external perspective view of the shaft 2. As shown in FIGS. 1 and 2, one end side of the shaft 2 is inserted into a hole provided in the center of the rotor 10. The other end of the shaft 2 protrudes outward from the motor unit 3 and is directly connected to the rod 104 and is connected to the lever 105 on the turbocharger side. In the illustrated example, the shaft 2 and the rod 104 are integrated by fastening with bolts and nuts, but the present invention is not limited to this, and the shaft 2 may be connected to the lever 105 without using the rod 104. . On the outer peripheral surface on one end side of the shaft 2, a male screw portion 2 a that is screwed into the female screw portion 10 a of the rotor 10 is formed.
- the outer peripheral surface of the shaft 2 is deformed to form a rotation preventing portion 2b and a retaining portion 2c, and a columnar cylindrical portion 2e is formed at the tip side of the retaining portion 2c. Is formed.
- the diameter of the shaft 2 is enlarged to form a retaining portion 2c, and the enlarged portion is formed into a long cross section to provide two planar portions, and these planar portions are respectively used as the rotation preventing portions 2b.
- the corners of the end face of the retaining portion 2c are rounded into a curved surface 2d.
- the portion of the shaft 2 protruding from the rotor 10 is accommodated in the shaft housing 14.
- the shaft housing 14 is fixed to one end side of the motor housing 6. Further, on the side near the rotor 10 of the shaft housing 14, there is formed a detent guide portion 14 a that engages with the detent portion 2 b of the shaft 2 to prevent the rotation of the shaft 2, and the shaft 2 is arranged on the opposite side.
- a boss (first sliding support portion) 14b that is slidably supported in the linear motion direction X is formed. Further, a seal member 15 such as an O-ring is fitted and inserted adjacent to the boss 14b, and a cap (second sliding support portion) 16 is fixed to the shaft housing 14 by welding or the like adjacent to the seal member 15. Yes.
- the seal member 15 is held with respect to the shaft housing 14 by sandwiching the seal member 15 between the cap 16 and the boss 14b. Further, the cylindrical portion 2e of the shaft 2 is inserted into the circular holes of the cap 16 and the boss 14b, and the cylindrical portion 2e is slidably supported.
- FIG. 3 is a cross-sectional view showing the configuration of the shaft 2 and the shaft housing 14.
- FIG. 3 (a) is a view taken along the line II in FIG. 1
- FIG. 3 (b) is a view taken along the line II-II
- FIG. ) Is the III-III arrow view.
- the shaft housing 14 is shaped like a long hole in cross section, and two straight portions are provided, and these straight portions are used as the rotation preventing guide portion 14a.
- the rotation preventing portion 2b slides on the rotation preventing guide portion 14a, thereby restricting the shaft 2 from rotating in accordance with the rotation of the rotor 10 and supporting the movement of the shaft 2 in the linear motion direction X. .
- the end surface of the retaining portion 2c is a curved surface 2d, wear can be reduced when the retaining portion 2c slides on the non-rotating guide portion 14a.
- FIG. 3 (b) when the cylindrical portion 2e of the shaft 2 is positioned in the detent guide portion 14a, a gap is generated on both sides of the long hole.
- FIG. 3 (c) on the distal end side of the shaft housing 14, the cylindrical portion 2e of the shaft 2 is inserted into a hole having a circular cross section of the boss 14b, and supported so as to be slidable in the linear motion direction X.
- the swing of the rod 104 accompanying the rotational displacement of the lever 105 is transmitted to the shaft 2, but the cylindrical portion 2 e of the shaft 2 is supported at two locations of the boss 14 b and the cap 16.
- the load in the swing direction Y can be received by the boss 14b and the cap 16, and the swing can be suppressed. Therefore, the seal member 15 is not deformed by receiving a load in the swing direction Y of the shaft 2, and the sealing performance is not impaired.
- FIG. 4 is an enlarged cross-sectional view of the distal end side of the shaft housing 14.
- the retaining portion 2c abuts against the boss 14b as shown in FIG. There is no escape.
- the shaft housing 14 is firmly attached to the motor housing 6, even if the boss 14b is pushed by the retaining portion 2c, the shaft housing 14 formed integrally with the boss 14b is detached from the motor housing 6. There is nothing.
- the boss 14b is formed integrally with the shaft housing 14, it is difficult to be deformed even if it is pushed by the retaining portion 2c. Therefore, the sealing member 15 is not pressed and deformed by the boss 14b.
- the boss 14b is not easily deformed and the shaft 2 is supported at the two locations of the boss 14b and the cap 16, the shakiness of the shaft 2 due to vehicle vibration or the like can be suppressed.
- the bush 102 is configured separately from the housing 100 as in the prior art example shown in FIG. 5 described above, the bush 102 is deformed when it is pressed against the retaining portion 2c, and rattling occurs. It can happen. Further, since the turbo actuator 1 becomes hot, rattling of the bush 102 occurs even when the linear expansion coefficients of the housing 100 and the bush 102 are different. Therefore, the swing of the shaft 101 cannot be suppressed. Further, the bush 102 is easily pulled out of the housing 100 by being pressed by the retaining portion 2c. Furthermore, there is a possibility that the bush 102 pressed against the retaining portion 2c presses and deforms the adjacent seal member 103, thereby impairing the sealing performance.
- the turbo actuator 1 is arranged so as to be rotatable inside the stator 4 and the stator 4, and the rotor having the female screw portion 10a formed in the hole provided in the center.
- a male screw portion 2 a that is screwed into the female screw portion 10 a at one end portion, a columnar cylindrical portion 2 e at the other end portion, and a rotation preventing portion 2 b that deforms the outer surface therebetween, are formed to rotate the rotor 10.
- An anti-rotation guide portion 14a that contains the shaft 2 that linearly moves by converting into linear linear motion and the shaft 2 that protrudes from the rotor 10 and that engages with the anti-rotation portion 2b to prevent rotation of the shaft 2.
- a shaft housing 14 formed with a boss 14b that slidably supports the cylindrical portion 2e of the shaft 2, and the shaft housing 14 is fitted into the shaft housing 14 to close a gap between the shaft housing 14 and the cylindrical portion 2e of the shaft 2.
- a seal member 15 is fixed to the shaft housing 14, while clamping the seal member 15 between the boss 14b, and configured to include a cap 16 for slidably supporting the cylindrical portion 2e of the shaft 2. For this reason, the load of the shaft 2 is received at two locations of the boss 14 b and the cap 16, and the swing of the shaft 2 accompanying the rotation of the turbo lever 105 can be suppressed.
- the boss 14b is formed integrally with the shaft housing 14, it is possible to prevent the boss 14b from being deformed and rattling. Thus, deformation of the seal member 15 adjacent to the boss 14b can be prevented, and the shaft 2 can be slidably supported without impairing the sealing performance.
- the shaft housing 14 and the boss 14b are integrally formed, the number of parts can be reduced and the cost can be reduced. Further, since the cylindrical portion 2e of the shaft 2 is sealed, a general-purpose part such as an O-ring can be used as the seal member 15 and the cost is not increased.
- the diameter of the shaft 2 is enlarged to form the retaining portion 2c that contacts the boss 14b of the shaft housing 14, and the end surface corner portion of the retaining portion 2c is rounded to obtain the curved surface 2d. I made it. For this reason, when the shaft 2 moves linearly, it is possible to reduce wear on the shaft housing 14 side at the corner portion of the retaining portion 2c that slides on the rotation guide portion 14a of the shaft housing 14.
- the turbo actuator 1 is configured to drive the lever for opening and closing the wastegate valve of the turbocharger.
- the turbo actuator 1 is attached to a VG turbo. It may be configured to be mounted and to drive a nozzle vane opening / closing lever.
- the turbo actuator according to the present invention is used for the turbo actuator that drives the turbo side lever because the swing of the shaft is suppressed and slidably supported without impairing the sealing performance.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
Description
このアクチュエータをターボチャージャに搭載する場合、シャフト101の端部にロッド104が連結され、ロッド104の先端とレバー105の一端がピン軸106により屈曲自在に取り付けられる。このレバー105の他端側の支点107は、図6に示す排気バイパス通路108内のウェストゲートバルブ109に接続されている。図6に示すように、排気タービン上流側のエンジンから排気通路110へ排気ガスが流れて排気タービンへ導入されるが、一部の排気ガスを排気タービン下流側へ逃がして過給圧を制御する目的で、排気通路110にウェストゲート111を開設する。このウェストゲート111から排気バイパス通路108に流れた排気ガスは、排気タービンを迂回して下流側へ導入される。このとき、シャフト101の直動によりレバー105を支点107を中心に回動させることで、ウェストゲートバルブ109を回動させてウェストゲート111を開閉し、過給圧を制御する。
さらに、上記特許文献1では、シャフト101の径を拡大した肩部をブッシュ102に衝突させることによって、異常動作時のシャフト101の直動を規制する構成になっているため、衝突の力によりブッシュ102がシール部材103を変形してシール性を損なう場合があった。また、衝突の力により、ブッシュ102とシール部材103がハウジング100から抜け出る可能性もあった。
実施の形態1.
図1に示すターボ用アクチュエータ1は、主に、ターボチャージャ側のレバー105を駆動するシャフト2と、このシャフト2を直動方向Xへ直線移動させるモータ部3とを備える。なお、シャフト2の先端側には、ロッド104を取り付け、ロッド104の先端にレバー105を屈曲自在に取り付けて、直動方向Xの移動量に応じてウェストゲートバルブ109(図6に示す)の弁開度を制御する。
シャフト2の一端側の外周面には、回転子10の雌ネジ部10aに螺合する雄ネジ部2aが形成されている。また、シャフト2の中央部には、このシャフト2の外周面を変形して回り止め部2bと抜け止め部2cとが形成され、抜け止め部2cより先端側には円柱形状の円柱部2eが形成されている。図示例では、シャフト2の径を拡大して抜け止め部2cにし、さらに拡大部分を断面長尺状にして2箇所の平面部分を設け、これら平面部分をそれぞれ回り止め部2bにする。また、抜け止め部2cの端面角部を丸めて曲面2dにする。
図3(a)に示すように、シャフトハウジング14を断面長穴状にして2箇所の直線部分を設けて、これら直線部分を回り止めガイド部14aにする。回り止め部2bが回り止めガイド部14aを摺動することにより、回転子10の回転に合わせてシャフト2が回転運動するのを規制し、シャフト2が直動方向Xへ移動することをサポートする。また、抜け止め部2cの端面を曲面2dにしたので、抜け止め部2cが回り止めガイド部14aを摺動するときに磨耗を軽減させることができる。
図3(b)に示すように、回り止めガイド部14aにシャフト2の円柱部2eが位置しているときは、長穴の両側に隙間が生じている。
図3(c)に示すように、シャフトハウジング14の先端側では、ボス14bの断面円形の穴に、シャフト2の円柱部2eを挿通して、直動方向Xへ摺動可能に支持する。
ターボ用アクチュエータ1に電圧が印加されると、固定子4に巻回されたコイル5に電流が流れ、複数の極に分極された固定子4がNS磁化する。それにより、NS着磁されたマグネット11の装着された回転子10が回転し、雌ネジ部10aに螺合している雄ネジ部2aが駆動力を受けて、シャフト2が回転子10の外へ突出する方向へ移動する。このとき、シャフト2の回り止め部2bがシャフトハウジング14の回り止めガイド部14aを摺動するので、シャフト2が回転することなく直動方向Xへ直線移動する。すると、シャフト2に直結したロッド104がレバー105の一端を押圧するので、レバー105が支点107を中心に回動してウェストゲートバルブ109(図6に示す)を開弁する。
また、シャフトハウジング14がモータハウジング6に強固に取り付いているので、ボス14bが抜け止め部2cに押されたとしても、このボス14bと一体に形成されているシャフトハウジング14がモータハウジング6から外れることはない。さらに、ボス14bは、シャフトハウジング14に一体に形成されているので、抜け止め部2cに押されても変形し難い。よって、ボス14bによってシール部材15が押圧され変形することもない。また、ボス14bが変形し難く、かつ、ボス14bとキャップ16の2箇所でシャフト2を支持しているので、車両の振動等によるシャフト2のがたつきを抑制できる。
また、上記説明では、ターボ用アクチュエータ1がターボチャージャのウェストゲートバルブ開閉用のレバーを駆動する構成にしたが、これに限定されるものではなく、その他にも例えばVGターボにターボ用アクチュエータ1を搭載してノズルベーン開閉用のレバーを駆動する構成にしてもよい。
Claims (2)
- 固定子と、
前記固定子の内側に回転可能に配置され、中心に設けた穴に雌ネジ部が形成された回転子と、
一端部に前記雌ネジ部に螺合する雄ネジ部、他端部に円柱形状の円柱部、その間の外面を変形した回り止め部が形成され、前記回転子の回転を軸方向の直線運動に変換して直線移動するシャフトと、
前記回転子から突出する前記シャフトを内包し、前記回り止め部に係合して前記シャフトの回転を防止する回り止めガイド部、および前記シャフトの円柱部を摺動可能に支持する第1摺動支持部が形成されたシャフトハウジングと、
前記シャフトハウジングに嵌挿され、前記シャフトハウジングと前記シャフトの円柱部との隙間を塞ぐシール部材と、
前記シャフトハウジングに固定され、前記第1摺動支持部との間に前記シール部材を挟持すると共に、前記シャフトの円柱部を摺動可能に支持する第2摺動支持部とを備えるターボ用アクチュエータ。 - 前記シャフトハウジング内の前記シャフトの径を拡大して、前記第1摺動支持部に当接する抜け止め部を形成し、当該抜け止め部の端面角部を曲面状にしたことを特徴とする請求項1記載のターボ用アクチュエータ。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2013540494A JP5710018B2 (ja) | 2011-10-24 | 2011-10-24 | ターボ用アクチュエータ |
DE112011105757.1T DE112011105757B4 (de) | 2011-10-24 | 2011-10-24 | Turboaktor |
PCT/JP2011/005933 WO2013061357A1 (ja) | 2011-10-24 | 2011-10-24 | ターボ用アクチュエータ |
CN201180072532.0A CN103703224B (zh) | 2011-10-24 | 2011-10-24 | 涡轮用致动器 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2011/005933 WO2013061357A1 (ja) | 2011-10-24 | 2011-10-24 | ターボ用アクチュエータ |
Publications (1)
Publication Number | Publication Date |
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WO2013061357A1 true WO2013061357A1 (ja) | 2013-05-02 |
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ID=48167230
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2011/005933 WO2013061357A1 (ja) | 2011-10-24 | 2011-10-24 | ターボ用アクチュエータ |
Country Status (4)
Country | Link |
---|---|
JP (1) | JP5710018B2 (ja) |
CN (1) | CN103703224B (ja) |
DE (1) | DE112011105757B4 (ja) |
WO (1) | WO2013061357A1 (ja) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20160003135A1 (en) * | 2013-02-11 | 2016-01-07 | Continental Automotive Gmbh | Turbocharger Comprising a Regulating Unit |
WO2016162923A1 (ja) * | 2015-04-06 | 2016-10-13 | 三菱電機株式会社 | ウエストゲートアクチュエータおよびウエストゲートバルブ駆動装置 |
JP2016200257A (ja) * | 2015-04-14 | 2016-12-01 | Kybモーターサイクルサスペンション株式会社 | アジャスタ装置およびフロントフォーク |
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- 2011-10-24 DE DE112011105757.1T patent/DE112011105757B4/de not_active Expired - Fee Related
- 2011-10-24 CN CN201180072532.0A patent/CN103703224B/zh active Active
- 2011-10-24 JP JP2013540494A patent/JP5710018B2/ja active Active
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US20160003135A1 (en) * | 2013-02-11 | 2016-01-07 | Continental Automotive Gmbh | Turbocharger Comprising a Regulating Unit |
US10240517B2 (en) * | 2013-02-11 | 2019-03-26 | Continental Automotive Gmbh | Turbocharger comprising a regulating unit |
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JPWO2016162923A1 (ja) * | 2015-04-06 | 2017-06-29 | 三菱電機株式会社 | ウエストゲートアクチュエータおよびウエストゲートバルブ駆動装置 |
CN107429605A (zh) * | 2015-04-06 | 2017-12-01 | 三菱电机株式会社 | 旁通阀致动器及旁通阀驱动装置 |
JP2016200257A (ja) * | 2015-04-14 | 2016-12-01 | Kybモーターサイクルサスペンション株式会社 | アジャスタ装置およびフロントフォーク |
WO2017037870A1 (ja) * | 2015-09-01 | 2017-03-09 | 三菱電機株式会社 | アクチュエータとその調整方法 |
JPWO2017037870A1 (ja) * | 2015-09-01 | 2017-12-28 | 三菱電機株式会社 | アクチュエータとその調整方法 |
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Also Published As
Publication number | Publication date |
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JP5710018B2 (ja) | 2015-04-30 |
CN103703224B (zh) | 2016-01-20 |
DE112011105757B4 (de) | 2016-05-19 |
JPWO2013061357A1 (ja) | 2015-04-02 |
DE112011105757T5 (de) | 2014-11-06 |
CN103703224A (zh) | 2014-04-02 |
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