WO2016162923A1 - 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 - Google Patents
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 Download PDFInfo
- Publication number
- WO2016162923A1 WO2016162923A1 PCT/JP2015/060741 JP2015060741W WO2016162923A1 WO 2016162923 A1 WO2016162923 A1 WO 2016162923A1 JP 2015060741 W JP2015060741 W JP 2015060741W WO 2016162923 A1 WO2016162923 A1 WO 2016162923A1
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- WIPO (PCT)
- Prior art keywords
- shaft
- motor
- valve
- wastegate
- 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
- F02B37/18—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
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
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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
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
- F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
- F16K1/20—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation arranged externally of valve member
- F16K1/2007—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation arranged externally of valve member specially adapted operating means therefor
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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
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
- F16K31/041—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves
- F16K31/042—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves with electric means, e.g. for controlling the motor or a clutch between the valve and the motor
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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
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
- F16K31/041—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves
- F16K31/043—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means
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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
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/44—Mechanical actuating means
- F16K31/50—Mechanical actuating means with screw-spindle or internally threaded actuating means
- F16K31/508—Mechanical actuating means with screw-spindle or internally threaded actuating means the actuating element being rotatable, non-rising, and driving a non-rotatable axially-sliding element
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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
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K37/00—Special means in or on valves or other cut-off apparatus for indicating or recording operation thereof, or for enabling an alarm to be given
- F16K37/0025—Electrical or magnetic means
- F16K37/0041—Electrical or magnetic means for measuring valve parameters
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02P—CONTROL OR REGULATION OF ELECTRIC MOTORS, ELECTRIC GENERATORS OR DYNAMO-ELECTRIC CONVERTERS; CONTROLLING TRANSFORMERS, REACTORS OR CHOKE COILS
- H02P6/00—Arrangements for controlling synchronous motors or other dynamo-electric motors using electronic commutation dependent on the rotor position; Electronic commutators therefor
- H02P6/28—Arrangements for controlling current
-
- 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 WG actuator and a WG valve driving device for opening and closing a wastegate (hereinafter referred to as WG) valve of a turbocharger mounted on a vehicle.
- WG wastegate
- the turbocharger is configured to rotate the turbine with exhaust gas from the engine, drive a compressor connected coaxially with the turbine, compress the intake air, and supply the compressed air to the engine.
- a WG valve that releases exhaust gas from the exhaust passage to the bypass passage is installed in front of the turbine in the exhaust passage, and the WG actuator opens and closes the WG valve to adjust the amount of exhaust gas flowing from the exhaust passage to the bypass passage.
- the rotational speed of the turbine is controlled (see, for example, Patent Document 1).
- the torque of the DC motor is transmitted to the WG valve via the spur gear, and the amount of exhaust gas flowing into the bypass passage is adjusted by adjusting the opening of the WG valve. Since the pressure of the exhaust gas flowing through the exhaust passage is applied in the valve opening direction of the WG valve, it is necessary to always energize the DC motor in order to maintain the opening degree of the WG valve. When the WG valve is fully closed, the exhaust gas pressure applied to the WG valve becomes the largest, so it is necessary to increase the energization current to the DC motor, and there is a problem that an excessive current is required. .
- the present invention has been made to solve the above-described problems, and an object of the present invention is to reduce the current of the DC motor necessary for maintaining the position of the shaft in the WG actuator.
- a WG actuator according to the present invention includes a direct current motor, a shaft that opens and closes a WG valve of a turbocharger, and a screw mechanism that converts the rotational motion of the direct current motor into linear motion of the shaft. This is an angle corresponding to the current of the DC motor necessary for maintaining the position of the motor.
- the torque of the DC motor is transmitted to the WG valve via the screw mechanism, it is possible to reduce the current of the DC motor by using the friction force generated in the screw mechanism for maintaining the position of the shaft. it can. Further, by setting the lead angle of the screw mechanism to an angle corresponding to the current of the DC motor necessary for maintaining the position of the shaft, the current to the DC motor can be adjusted when designing the WG actuator. In the WG actuator that employs a small lead angle, the current of the DC motor necessary for maintaining the shaft position can be reduced as compared with the WG actuator that employs a large lead angle.
- FIG. 3 is an enlarged cross-sectional view of a screw mechanism of the WG actuator according to Embodiment 1.
- FIG. It is a figure explaining the lead angle of the screw mechanism of the WG actuator concerning Embodiment 1.
- FIG. 4 (a) shows the example which made the external thread part the short lead
- FIG.4 (b) shows the example made into the long lead.
- FIG. 1 is a cross-sectional view illustrating a configuration example of a WG actuator 1 according to the first embodiment.
- the turbocharger has a configuration in which a turbine is rotated by exhaust gas from an engine, a compressor connected coaxially with the turbine is driven, and intake air is compressed and supplied to the engine.
- a WG valve 2 for allowing exhaust gas to escape from the exhaust passage 100 to the bypass passage 101 is installed on the upstream side of the exhaust passage 100.
- the WG actuator 1 opens and closes the WG valve 2 to open the exhaust passage 100 to the bypass passage 101.
- the rotational speed of the turbine is controlled by adjusting the exhaust gas inflow amount.
- the fully closed state of the WG valve 2 is indicated by a solid line
- the fully open state is indicated by a two-dot chain line.
- the WG actuator 1 includes a DC motor 4 serving as a drive source, a shaft 13 that opens and closes the WG valve 2, and a screw mechanism 12 that converts the rotational motion of the DC motor 4 into linear motion of the shaft 13.
- the DC motor 4 includes a rotor 6 having a plurality of magnets 5 magnetized in N and S poles, and a stator 8 around which a coil 7 is wound.
- a brush 11 b is connected to the end of the coil 7.
- One end side of the rotor 6 is rotatably supported by a bearing portion 14, and a commutator 9 is fixed to the other end side.
- the rotor 6 has a hole for arranging the shaft 13, a female screw portion 12 a is formed on the inner peripheral surface of the hole, and a male screw portion 12 b is formed on the outer peripheral surface of the shaft 13.
- the male threaded portion 12b is screwed into the female threaded portion 12a and coupled to convert the rotational motion of the rotor 6 into the linear motion of the shaft 13.
- the female screw portion 12a and the male screw portion 12b constitute a screw mechanism 12.
- One end side of the shaft 13 passes through the housing 15 and is connected to the WG valve 2 via the link mechanism 3.
- a position sensor 16 for detecting the position of the shaft 13 in the axial direction is installed.
- the link mechanism 3 has two plates 3a and 3b.
- a shaft 13 is attached to one end side of the plate 3a, and one end side of the plate 3b is rotatably attached to a fulcrum 3c on the other end side.
- the WG valve 2 is attached to the other end of the plate 3b.
- the shaft 13 is formed with two planes and functions as the rotation restricting portion 13a.
- a guide portion 15a such as a two-plane is formed on the inner peripheral surface of the hole of the housing 15 that penetrates the shaft 13 in accordance with the shape of the rotation restricting portion 13a.
- a stopper 15b that protrudes toward the shaft 13 is formed at the end of the guide portion 15a.
- a plate that functions as the stopper 15c is installed at the end of the screw mechanism 12, and the end surface of the shaft 13 that functions as the abutting portion 13c abuts against the stopper 15c, so that the shaft 13 is further closed in the valve closing direction. Restrict movement.
- a hole that is smaller than the outer diameter of the shaft 13 passes through the plate that functions as the stopper 15 c of the shaft 13, and the sensor shaft 17 is passed through the hole, and the end surface of the sensor shaft 17 contacts the end surface of the shaft 13. Touch. Accordingly, the sensor shaft 17 also reciprocates in accordance with the axial reciprocation of the shaft 13.
- a sensor magnet 18 is fixed to the sensor shaft 17, and the magnetic flux density passing through the position sensor 16 is also changed by changing the position of the sensor magnet 18 with respect to the position sensor 16 as the shaft 13 reciprocates. Change.
- the position sensor 16 is a Hall element, a magnetoresistive element, or the like, detects a magnetic flux density that changes as the shaft 13 reciprocates, converts it to an electric signal indicating the actual stroke position of the shaft 13, and outputs it to the control device 20. To do.
- the control device 20 receives the actual stroke position of the shaft 13 from the position sensor 16. Further, the control device 20 receives the target stroke position of the shaft 13 from an engine control unit (not shown) or the like. Then, the control device 20 performs feedback control so that the actual stroke position approaches the target stroke position, adjusts the energization current to the DC motor 4, and generates a torque proportional to the energization current to move and maintain the position of the shaft 13. I do.
- the torque and energization current necessary for holding the position of the shaft 13 are referred to as holding torque and holding current.
- the control device 20 is realized by a processing circuit such as a CPU or a system LSI that executes a program stored in a memory.
- the control device 20 is configured as an independent electronic control unit.
- the control device 20 may be configured to be realized as a function of an engine control unit (not illustrated), or may be configured as a circuit board inside the WG actuator 1. May be incorporated.
- FIG. 2 is an enlarged view of the screw mechanism 12 of the WG actuator 1, and shows a cross section of the female screw portion 12a and the male screw portion 12b.
- D is an effective diameter of the female screw portion 12a and the male screw portion 12b.
- L is the lead of the female screw portion 12a and the male screw portion 12b, and is the distance that the male screw portion 12b of the shaft 13 advances in the axial direction while the female screw portion 12a of the rotor 6 makes one rotation.
- FIG. 3 is a diagram for explaining the lead angle ⁇ of the screw mechanism 12.
- the lead angle ⁇ is an angle of the inclined surface 12c, that is, an angle with respect to the radial direction of the spiral thread.
- a force of W cos ⁇ is applied perpendicularly to the inclined surface 12c.
- the male screw portion 12b tries to slide toward the lower side of the slope 12c with the force of Wsin ⁇ , and a frictional force of ⁇ W cos ⁇ is generated toward the upper side of the slope 12c.
- ⁇ is a friction coefficient of the inclined surface 12c.
- valve opening force Since the exhaust gas pressure in the valve opening direction (hereinafter referred to as “valve opening force”) is applied to the WG valve 2, a load W is also applied to the shaft 13 connected to the WG valve 2 in the valve opening direction.
- the frictional force ⁇ W cos ⁇ acts between the 13 male screw portions 12 b and the female screw portion 12 a of the rotor 6, the shaft 13 becomes difficult to rotate. That is, by providing the screw mechanism 12, the valve opening force of the exhaust gas applied to the shaft 13 can be reduced.
- the force that holds the position of the shaft 13 against the valve opening force of the exhaust gas is substantially equal to the total force of the friction force generated in the screw mechanism 12 and the holding torque of the DC motor 4. If the force increases, the holding torque of the DC motor 4 can be reduced accordingly, and the holding current can be reduced. Therefore, the torque of the DC motor 4 is transmitted to the WG valve 2 via the screw mechanism 12 as in the first embodiment, compared to the conventional configuration in which the torque of the DC motor 4 is transmitted to the WG valve 2 via the spur gear.
- the configuration of transmitting to the DC motor 4 can reduce the energization current to the DC motor 4.
- the frictional force ⁇ W cos ⁇ is increased, so that the holding torque necessary for holding the position of the shaft 13 against the load W is reduced, and the holding current can be reduced.
- the frictional force ⁇ W cos ⁇ is decreased, so that a large holding torque is required and the holding current is also increased.
- FIG. 4A and 4B are views for explaining the lead L of the screw mechanism 12.
- FIG. 4A shows an example in which the male screw portion 12b has a small lead angle ⁇ , that is, a short lead L
- FIG. 4B shows a large lead angle.
- An example of ⁇ , that is, a long lead L is shown.
- FIG. 4 shows the male screw portion 12b, the same applies to the female screw portion 12a. Since the lead L of the male screw portion 12b having a small lead angle ⁇ is short, the speed at which the shaft 13 moves linearly becomes slower than the speed at which the rotor 6 rotates, and the responsiveness decreases. On the contrary, since the male lead portion 12b having a large lead angle ⁇ has a long lead L, the speed at which the shaft 13 moves linearly with respect to the speed at which the rotor 6 rotates is increased, and the responsiveness is improved.
- the lead angle of the screw mechanism 12 is determined so as to satisfy a desired holding current and response when the WG actuator 1 is designed. Note that the pressure of the exhaust gas flowing through the exhaust passage 100 varies with time, and the exhaust gas pressure applied to the WG valve 2 varies depending on the opening of the WG valve 2, so that, for example, the lead angle corresponding to the average value of the holding current Or a lead angle corresponding to the maximum value of the holding current may be selected.
- the lead angle of the male screw portion 12b is selected so that the friction coefficient ⁇ of the inclined surface 12c of the screw mechanism 12 and the lead angle ⁇ satisfy ⁇ > tan ⁇ .
- the frictional force ⁇ W cos ⁇ is greater than the sliding force W sin ⁇ and the shaft 13 does not rotate, so the holding current can be made zero.
- the control device 20 determines that the shaft 13 is retracted to the fully closed position of the WG valve 2 on the basis of the actual stroke position of the shaft 13 detected by the position sensor 16, it is determined in advance from the determination time.
- the energizing current to the DC motor 4 is maintained until the elapsed time elapses, and the rotor 6 is rotated in a state where the abutting portion 13c of the shaft 13 is in contact with the stopper 15c, and the screw mechanism 12 is further tightened.
- the frictional force between the female screw portion 12a and the male screw portion 12b is increased, and the shaft 13 is difficult to rotate even when a load W is applied.
- the holding current can be reduced. It is assumed that the above predetermined time is stored in advance in a memory in the control device 20.
- the WG actuator 1 shown in FIG. 1 has a configuration in which the shaft 13 is pulled in and the WG valve 2 is closed. On the contrary, in the configuration in which the shaft 13 is pushed out and the WG valve 2 is closed, the control is performed.
- the apparatus 20 determines that the shaft 13 has been pushed out to the fully closed position of the WG valve 2, it maintains the energization current to the DC motor 4 for a predetermined time, and the abutting portion 13b of the shaft 13 serves as the stopper 15b.
- the rotor 6 is rotated in the contact state, and the screw mechanism 12 is further tightened.
- the WG actuator 1 includes the DC motor 4, the shaft 13 that opens and closes the WG valve 2 of the turbocharger, and the screw that converts the rotational motion of the DC motor 4 into the linear motion of the shaft 13. Since the mechanism 12 is provided, the frictional force generated in the screw mechanism 12 can be used for holding the position of the shaft 13 to reduce the holding current to the DC motor 4. Further, by adjusting the lead angle of the screw mechanism 12 to an angle corresponding to the holding current of the DC motor 4 necessary for holding the position of the shaft 13, the holding current to the DC motor 4 can be adjusted when the WG actuator 1 is designed. Can do. In the WG actuator 1 that employs a small lead angle, the holding current required to maintain the position of the shaft 13 can be reduced compared to the WG actuator 1 that employs a large lead angle.
- the lead angle of the screw mechanism 12 is made smaller than the friction angle, so that the shaft 13 does not rotate even when the exhaust gas pressure is received, and the holding current to the DC motor 4 becomes zero. it can.
- the WG actuator 1 includes the stopper 15c that regulates the linear motion of the shaft 13 at the position where the WG valve 2 is fully closed, and the control device 20 is when the WG valve 2 is fully closed.
- the WG valve 2 is fully closed by maintaining the current of the DC motor 4 necessary for the linear motion of the shaft 13 until a predetermined time elapses while the shaft 13 is regulated by the stopper 15c. In this case, the frictional force of the screw mechanism 12 can be increased. Thereby, the holding current required for holding the shaft 13 in the fully closed position of the WG valve 2 can be reduced.
- the shaft 13 and the WG valve 2 of the WG actuator 1 according to the present invention are connected using the link mechanism 3, but the shaft 13 and the WG valve are directly connected without using the link mechanism 3. 2 may be connected.
- you may comprise as a WG valve drive device provided with the WG actuator 1 which concerns on this invention, and the WG valve 2 which is a drive target object.
- the present invention can be modified with any component of the embodiment or omitted with any component.
- the WG actuator according to the present invention can reduce the current flowing to the DC motor, it is suitable for use in an actuator mounted on a vehicle.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Power Engineering (AREA)
- Supercharger (AREA)
- Electrically Driven Valve-Operating Means (AREA)
- Transmission Devices (AREA)
Abstract
Description
実施の形態1.
図1は、実施の形態1に係るWGアクチュエータ1の構成例を示す断面図である。ターボチャージャは、エンジンからの排気ガスによってタービンを回転させ、このタービンと同軸で接続されたコンプレッサを駆動して吸気を圧縮しエンジンに供給する構成である。排気通路100のタービン上流側には、排気ガスを排気通路100からバイパス通路101へ逃がすWGバルブ2が設置されており、WGアクチュエータ1がWGバルブ2を開閉して排気通路100からバイパス通路101への排気ガス流入量を調整することにより、タービンの回転数を制御する。なお、図1では、WGバルブ2の全閉状態を実線で示し、全開状態を二点鎖線で示す。
なお、図1では直流モータ4としてブラシ付きDCモータを使用しているが、ブラシレスDCモータを使用してもよい。
ここでは、図1に示したWGアクチュエータ1において、WGバルブ2の全閉位置までシャフト13をハウジング15内に引き込んだときに、ストッパ15cと当て部13cとが当接してシャフト13の移動を規制する構成とする。この構成において、制御装置20は、位置センサ16により検出されるシャフト13の実ストローク位置に基づいて、WGバルブ2の全閉位置までシャフト13を引き込んだと判定したとき、判定時から予め定められた時間が経過するまでのあいだ直流モータ4への通電電流を維持して、当該シャフト13の当て部13cがストッパ15cに当接した状態でロータ6を回転させてネジ機構12を増し締めする。これにより、雌ネジ部12aと雄ネジ部12bの間の摩擦力が大きくなり、負荷Wがかかったとしてもシャフト13は回転しにくくなる。よって、上述の予め定められた時間が経過した後、シャフト13をWGバルブ2の全閉位置に保持する際、保持電流を小さくできる。なお、上述の予め定められた時間は、制御装置20内のメモリに予め記憶されているものとする。
また、本発明に係るWGアクチュエータ1と、駆動対象物であるWGバルブ2とを備えたWGバルブ駆動装置として構成してもよい。
Claims (5)
- 直流モータと、
ターボチャージャのウエストゲートバルブを開閉するシャフトと、
前記直流モータの回転運動を前記シャフトの直線運動に変換するネジ機構とを備え、
前記ネジ機構のリード角は、前記シャフトの位置保持に必要な前記直流モータの電流に応じた角度であることを特徴とするウエストゲートアクチュエータ。 - 前記ネジ機構のリード角は摩擦角より小さいことを特徴とする請求項1記載のウエストゲートアクチュエータ。
- 前記シャフトの位置を検出する位置センサと、
前記位置センサにより検出される前記シャフトの位置に基づいて前記直流モータへ通電する電流を調整する制御装置とを備えることを特徴とする請求項1記載のウエストゲートアクチュエータ。 - 前記ウエストゲートバルブが全閉する位置で前記シャフトの直線運動を規制するストッパを備え、
前記制御装置は、前記ウエストゲートバルブを全閉する場合、前記シャフトの直線運動に必要な前記直流モータの電流を、前記シャフトが前記ストッパに規制された状態で予め定められた時間が経過するまで維持することを特徴とする請求項3記載のウエストゲートアクチュエータ。 - 請求項1記載のウエストゲートアクチュエータと、
前記ウエストゲートアクチュエータによって駆動されるウエストゲートバルブとを備えることを特徴とするウエストゲートバルブ駆動装置。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201580077999.2A CN107429605B (zh) | 2015-04-06 | 2015-04-06 | 旁通阀致动器及旁通阀驱动装置 |
DE112015006422.2T DE112015006422B4 (de) | 2015-04-06 | 2015-04-06 | Wastegate-Stellantrieb und Wastegate-Ventil-Antriebseinrichtung |
JP2017510811A JP6320627B2 (ja) | 2015-04-06 | 2015-04-06 | 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 |
PCT/JP2015/060741 WO2016162923A1 (ja) | 2015-04-06 | 2015-04-06 | 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 |
US15/542,019 US20180003103A1 (en) | 2015-04-06 | 2015-04-06 | Wastegate actuator and wastegate valve driving device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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PCT/JP2015/060741 WO2016162923A1 (ja) | 2015-04-06 | 2015-04-06 | 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 |
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WO2016162923A1 true WO2016162923A1 (ja) | 2016-10-13 |
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Country Status (5)
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US (1) | US20180003103A1 (ja) |
JP (1) | JP6320627B2 (ja) |
CN (1) | CN107429605B (ja) |
DE (1) | DE112015006422B4 (ja) |
WO (1) | WO2016162923A1 (ja) |
Families Citing this family (12)
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JP2016089792A (ja) * | 2014-11-10 | 2016-05-23 | 大豊工業株式会社 | ウェイストゲートバルブ |
CN107509394B (zh) * | 2015-04-06 | 2021-04-09 | 三菱电机株式会社 | 致动器的控制装置、阀驱动装置及致动器的异常检测方法 |
US11639684B2 (en) | 2018-12-07 | 2023-05-02 | Polaris Industries Inc. | Exhaust gas bypass valve control for a turbocharger for a two-stroke engine |
US11828239B2 (en) | 2018-12-07 | 2023-11-28 | Polaris Industries Inc. | Method and system for controlling a turbocharged two stroke engine based on boost error |
US11725573B2 (en) | 2018-12-07 | 2023-08-15 | Polaris Industries Inc. | Two-passage exhaust system for an engine |
US20200182164A1 (en) | 2018-12-07 | 2020-06-11 | Polaris Industries Inc. | Method And System For Predicting Trapped Air Mass In A Two-Stroke Engine |
CN110173590B (zh) * | 2019-06-27 | 2020-05-05 | 爱诺阀门温州有限公司 | 一种双用执行器 |
CA3105239C (en) * | 2020-01-13 | 2023-08-01 | Polaris Industries Inc. | Turbocharger system for a two-stroke engine having selectable boost modes |
US11788432B2 (en) | 2020-01-13 | 2023-10-17 | Polaris Industries Inc. | Turbocharger lubrication system for a two-stroke engine |
US11434834B2 (en) | 2020-01-13 | 2022-09-06 | Polaris Industries Inc. | Turbocharger system for a two-stroke engine having selectable boost modes |
US11421619B2 (en) * | 2020-12-01 | 2022-08-23 | Garrett Transportation I Inc. | Wear monitoring for electrical actuators |
CN116045063B (zh) * | 2023-03-08 | 2023-06-20 | 江苏毅合捷汽车科技股份有限公司 | 用于多级涡轮增压器的排气旁通阀的连杆 |
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AU587220B2 (en) * | 1985-01-24 | 1989-08-10 | Honda Giken Kogyo Kabushiki Kaisha | Actuator for steering the rear wheels in front and rear wheel steering device for vehicle |
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2015
- 2015-04-06 JP JP2017510811A patent/JP6320627B2/ja active Active
- 2015-04-06 WO PCT/JP2015/060741 patent/WO2016162923A1/ja active Application Filing
- 2015-04-06 US US15/542,019 patent/US20180003103A1/en not_active Abandoned
- 2015-04-06 DE DE112015006422.2T patent/DE112015006422B4/de active Active
- 2015-04-06 CN CN201580077999.2A patent/CN107429605B/zh not_active Expired - Fee Related
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JPH03112337A (ja) * | 1989-09-25 | 1991-05-13 | Copal Electron Co Ltd | リニア モーション モータのエンドストップ機構 |
JPH08507347A (ja) * | 1993-11-11 | 1996-08-06 | アライドシグナル・リミテツド | 内燃機関用ターボチャージャ |
JP2011247398A (ja) * | 2010-05-31 | 2011-12-08 | Denso Corp | バルブ駆動装置 |
WO2013061357A1 (ja) * | 2011-10-24 | 2013-05-02 | 三菱電機株式会社 | ターボ用アクチュエータ |
Also Published As
Publication number | Publication date |
---|---|
JPWO2016162923A1 (ja) | 2017-06-29 |
DE112015006422B4 (de) | 2022-02-17 |
CN107429605B (zh) | 2019-11-01 |
JP6320627B2 (ja) | 2018-05-09 |
DE112015006422T8 (de) | 2018-01-25 |
DE112015006422T5 (de) | 2018-01-18 |
CN107429605A (zh) | 2017-12-01 |
US20180003103A1 (en) | 2018-01-04 |
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