WO2019241984A1 - 一种电动相位调节装置 - Google Patents

一种电动相位调节装置 Download PDF

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Publication number
WO2019241984A1
WO2019241984A1 PCT/CN2018/092318 CN2018092318W WO2019241984A1 WO 2019241984 A1 WO2019241984 A1 WO 2019241984A1 CN 2018092318 W CN2018092318 W CN 2018092318W WO 2019241984 A1 WO2019241984 A1 WO 2019241984A1
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WO
WIPO (PCT)
Prior art keywords
output wheel
driven gear
boss
casing
electric phase
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PCT/CN2018/092318
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English (en)
French (fr)
Inventor
陈鹏
邓猛
向明朗
胡荣
朱玉刚
Original Assignee
绵阳富临精工机械股份有限公司
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Publication date
Application filed by 绵阳富临精工机械股份有限公司 filed Critical 绵阳富临精工机械股份有限公司
Priority to PCT/CN2018/092318 priority Critical patent/WO2019241984A1/zh
Publication of WO2019241984A1 publication Critical patent/WO2019241984A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear

Definitions

  • the invention belongs to the technical field of automobile parts, and particularly relates to an electric phase adjustment device.
  • phase reduction mechanism is mostly used for phase adjustment, that is, the rotation direction of the motor relative to the casing is consistent with the phase adjustment direction.
  • the drag torque of the phase backward adjustment is smaller than that of the forward adjustment.
  • An object of the present invention is to provide an electric phase adjustment device that can not only reduce the axial size and weight, but also improve the work efficiency, and reduce the power of the motor.
  • An electric phase adjustment device includes: a motor and a phaser, and the rotation motion of the motor shaft of the motor is decelerated by the phaser to control the phase of the camshaft of the engine relative to the crankshaft;
  • the phaser comprises: a housing, a driven gear, an output wheel, a support frame and a floating disk; characterized in that: the housing rotates synchronously with the crankshaft of the engine; the driven gear is arranged inside the housing and its driven teeth And the driving tooth portion of the casing mesh with each other; the output wheel is disposed inside the casing and is rigidly connected to the engine camshaft and can rotate around the axis of the casing; the floating disk is disposed between the driven gear and the output Between the wheels, the floating disk can slide radially relative to the driven gear and the output wheel, respectively, and the driven gear, the floating disk, and the output wheel rotate synchronously; the support frame is disposed inside the casing and can rotate around the casing The body axis rotate
  • the outer part of the casing can be rotated synchronously with the engine crankshaft through a chain or a belt.
  • the inner part is provided with a cavity and a driving tooth.
  • the output wheel is supported, and the inner annular support surface is axially adjacent to the driving tooth portion and coincides with the axial direction of the casing.
  • the casing includes a sprocket, a driving ring gear, and a front cover plate, and the sprocket, the driving ring gear, and the front cover plate are locked together by a connecting member;
  • a driving tooth is formed inside the driving ring gear, and at least one sprocket limiting boss is provided on the sprocket.
  • the driven gear includes a driven tooth portion and a driven bearing, and a driven gear boss is provided on an end surface of one side of the driven gear, and the driven gear boss and The floating disc cooperates to transmit the rotary motion of the driven gear.
  • the driven gear includes a driven tooth portion and a driven bearing, and a driven gear slot is provided on an end face of the driven gear, and the driven gear slot Cooperate with floating disk for transmitting rotary motion of driven gear.
  • one end surface of the output wheel is rigidly connected to the engine camshaft, and at least one output wheel limiting boss is provided on the end surface, and the other side of the output wheel
  • An output wheel boss is provided on the end surface, and the output wheel boss cooperates with the floating disk to receive a rotational movement from the driven gear.
  • one end surface of the output wheel is rigidly connected to the engine camshaft, and at least one output wheel limiting boss is provided on the end surface, and the other side of the output wheel
  • An output wheel notch is provided on the end surface, and the output wheel notch cooperates with the floating disk and is used for receiving a rotational movement from the driven gear.
  • an oil passage is provided on an end surface of the output wheel connected to the engine camshaft, and a camshaft oil hole communicating with the oil passage is provided on the engine camshaft.
  • the output wheel is provided with an output wheel oil hole that communicates with the oil passage. The lubricating oil enters through the camshaft oil hole, flows through the oil passage, and enters the phaser through the output wheel oil hole.
  • the sprocket limiting bosses on the sprocket of the casing are arranged between the output wheel limiting bosses, and the adjustable angle of the phaser is limited by the sprocket.
  • the boss angle ⁇ and the angle ⁇ between the two output wheel limiting bosses are determined.
  • the support frame includes a central shaft, a support frame bearing, and an eccentric sleeve.
  • the axis lines of the inner circular surface and the outer circular surface of the eccentric sleeve are parallel to each other and do not overlap.
  • the frame bearing is arranged between the central shaft and the eccentric sleeve, and the eccentric sleeve can be eccentrically rotated relative to the central shaft.
  • the floating disk is provided with cross-shaped notches, which can be matched with the driven gear boss and the output wheel boss, respectively, and can slide freely in the radial direction.
  • cross-distributed branches are provided on the floating plate, which can be matched with the slot of the driven gear and the slot of the output wheel, respectively, and can slide freely in the radial direction.
  • the invention relates to the use of a motor and a planetary reducer to dynamically adjust the phase angle of a camshaft of an internal combustion engine with respect to a crankshaft, so as to adjust the timing of opening and closing of an engine valve, thereby improving the fuel efficiency of the internal combustion engine.
  • the device can not only reduce the axial size and weight Moreover, the efficiency of the phase adjustment device can be improved, at the same time, the working noise of the phase adjustment device can be reduced, and the service life can be extended.
  • FIG. 1 is a schematic structural diagram of the present invention.
  • FIG. 2 is a schematic diagram of the present invention.
  • 3 and 4 are schematic structural diagrams of a casing in the present invention.
  • 5 and 6 are schematic structural diagrams of two implementation examples of the driven gear in the present invention.
  • FIG. 7 is a schematic structural diagram of an oil tank of an output wheel in the present invention.
  • FIG 8 and 9 are schematic structural diagrams of two implementation examples of the output wheel in the present invention.
  • FIG. 10 is a schematic structural diagram of a support frame in the present invention.
  • 11 and 12 are schematic structural diagrams of two implementation examples of the floating disk in the present invention.
  • FIG. 13 is a schematic diagram of determining an adjustable angle of a phaser in the present invention.
  • FIG. 14 is a schematic view of gear meshing according to the present invention.
  • Reference signs: 1 is a motor, 2 is a phaser, 3 is an engine camshaft, 4 is a motor shaft, 401 is a camshaft oil hole, 5 is a housing, 501 is a sprocket, 502 is a driving ring gear, and 503 is a front Cover plate, 504 is a cavity, 505 is a driving gear, 506 is a sprocket limit boss, 6 is a driven gear, 601 is a driven gear, 602 is a driven bearing, and 603 is a driven gear boss, 604 is the driven gear boss plane, 605 is the driven gear notch, 7 is the output wheel, 701 is the output wheel limit boss, 702 is the output wheel boss, 703 is the output wheel boss plane, and 704 is the oil channel 705 is an output wheel oil hole, 706 is an output wheel slot, 8 is a support frame, 801 is a central shaft, 802 is a support frame bearing, 803 is an eccentric sleeve, 9 is a floating
  • an electric phase adjustment device includes a motor 1 and a phaser 2. After the rotation of the motor shaft 4 of the motor 1 is decelerated by the phaser 2, the phase of the engine camshaft 3 relative to the crankshaft is controlled.
  • the phaser 2 includes a casing 5, a driven gear 6, an output wheel 7, a support frame 8, and a floating disk 9.
  • the driven gear 6 is disposed inside the casing 5, and the driven gear 6 is driven by the driven gear 6.
  • the teeth 601 and the driving teeth 505 of the housing 5 mesh with each other.
  • the output wheel 7 is disposed inside the cavity 504 of the housing 5 and is rotatable about the axis of the housing 5.
  • the floating disk 9 is provided on the driven gear 6.
  • the floating disc 9 can slide in the radial direction relative to the driven gear 6 and the output wheel 7, respectively, and the driven gear 6, the floating disc 9 and the output wheel 7 rotate synchronously, and the support
  • the frame 8 is arranged inside the casing 5.
  • the axis of the central axis 801 of the support frame 8 coincides with the axis of the output wheel 7, and is connected to the output wheel 7 by a connecting member screw 11.
  • the motor shaft 3 drives the support frame 8 to rotate.
  • the driven gear 6 performs planetary motion around the support frame 8, and its rotation is transmitted to the output wheel 7 through the floating disk 9.
  • the exterior of the casing 5 is a sprocket structure, and a cavity 504 and a driving tooth 505 are provided inside the cavity 5, and the cavity 504 forms an internal annular support surface, and the internal annular support surface is in contact with the internal annular support surface.
  • the driving teeth 505 are axially adjacent and coincide with each other axially, and coincide with the axial direction of the housing 5.
  • the housing 5 includes a sprocket 501, a driving ring gear 502, and The front cover plate 503, the sprocket 501, the driving ring gear 502, and the front cover plate 503 are locked together by a connecting member 507.
  • the outer periphery of the sprocket 501 forms a sprocket structure, and the driving ring gear 502 forms a drive inside.
  • the tooth portion 505 is provided with a sprocket limiting boss 506 on the sprocket 501.
  • one embodiment of the driven gear 6 includes a driven tooth portion 601 and a driven bearing 602, and at least two driven gear protrusions are provided on an end surface of one side of the driven gear 6.
  • Table 603 the driven gear bosses 603 cooperate with the notches on the floating disk 9 for transmitting the rotational movement of the driven gear 6, wherein the driven gear bosses 603 are two and are evenly distributed
  • the driven gear boss 603 is composed of pins embedded in the end face of the driven gear 6, in order to prevent The pin is deformed due to excessive contact stress, and the driven gear boss 603 is symmetrically processed into two driven gear boss planes 604.
  • one embodiment of the driven gear 6 includes a driven tooth portion 601 and a driven bearing 602, and at least two driven gear grooves are provided on an end surface of one side of the driven gear 6.
  • Port 605 the driven gear slot 605 cooperates with the floating disk 9 and is used to transmit the rotational movement of the driven gear 6.
  • one embodiment of the output wheel 7 is: one end surface of the output wheel 7 is rigidly connected to the engine camshaft 4, and two output wheel limiting bosses 701 are provided on the end surface, At least two output wheel bosses 702 are provided on the other end surface of the output wheel 7.
  • the output wheel bosses 702 cooperate with the notches on the floating disk 9 for receiving torque from the driven gear 6.
  • the output wheel bosses 702 are two and are evenly distributed on the end face of the same side of the output wheel 7.
  • the output wheel bosses 702 are embedded in the end face of the output wheel 7 by pins. Composition, in order to prevent the pin from deforming due to excessive contact stress, the output wheel boss 702 is symmetrically processed into two output wheel boss planes 703.
  • one embodiment of the output wheel 7 is characterized in that one end surface of the output wheel 7 is rigidly connected to the engine camshaft 4, and At least one output wheel limiting boss 701 is provided on the end surface, and at least two output wheel notches 706 are provided on the other end surface of the output wheel 7.
  • the output wheel notches 706 cooperate with the floating disk 9 and It receives a rotational movement from the driven gear 6.
  • an oil passage 704 is provided on an end surface of the output wheel 7 connected to the engine camshaft 4.
  • the camshaft 4 of the engine is provided with a camshaft oil hole 401 communicating with the oil passage 704.
  • the output wheel 7 is provided with an output wheel oil hole 705 communicating with the oil passage 704.
  • the lubricating oil enters through the camshaft oil hole 401. It flows through the oil passage 704 and enters the phaser 2 through the output wheel oil hole 705.
  • the sprocket limit boss 506 on the sprocket 501 is disposed between two output wheel limit bosses 701, and the adjustable angle of the phaser 2 is determined by the sprocket limit boss.
  • the angle 506 and the angle ⁇ between the two output wheel limiting bosses 701 are determined.
  • the support frame 8 includes a central shaft 801, a support frame bearing 802, and an eccentric sleeve 803.
  • the axis lines of the inner circular surface and the outer circular surface of the eccentric sleeve 803 are not parallel to each other.
  • a frame bearing 802 is disposed between the central shaft 801 and an eccentric sleeve 803, and the eccentric sleeve 803 can be eccentrically rotated relative to the central shaft 801.
  • one embodiment of the floating disk 9 includes: the outer circumference of the floating disk 9 is provided with two driven gears corresponding to the driven gear bosses 603 provided on the driven gear 6.
  • a notch 901, the driven gear boss 603 is inserted into the driven gear slot 901, and two outputs corresponding to the output wheel boss 702 provided on the output wheel 7 are provided on the inner circumference of the floating disk 9
  • the wheel notch 902 is inserted into the output wheel notch 902, and the driven gear notch 901 and the output wheel notch 902 are arranged in a cross shape on the floating disk 9 and are evenly distributed.
  • one embodiment of the floating disk 9 includes: the floating disk (9) is provided with four branches (903, 904) distributed in a cross, and can be connected with the driven gear slot (605), respectively. It cooperates with the output wheel notch (706) and can slide freely in the radial direction.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

一种电动相位调节装置，包括电机（1）和相位器（2），相位器（2）包括壳体（5）、从动齿轮（6）、输出轮（7）、支撑架（8）和浮动盘（9），壳体（5）由曲轴驱动，从动齿轮（6）设置于壳体（5）内部，从动齿轮（6）的从动齿部（601）与壳体（5）的驱动齿部（505）相互啮合，输出轮（7）设置于壳体（5）的腔体内部且可绕壳体（5）轴线旋转，浮动盘（9）设置在从动齿轮（6）与输出轮（7）之间，支撑架（8）设置于壳体（5）内部，径向偏心支撑从动齿轮（6）。使用电机（1）和相位器（2）动态调节内燃机凸轮轴相对于曲轴的相位角，以调节发动机气门打开和关闭的时刻，提高内燃机燃油效率。

Description

一种电动相位调节装置 技术领域
本发明属于汽车零部件技术领域，特别涉及一种电动相位调节装置。
背景技术
一直以来，一般公知通过油压调节凸轮轴相对曲轴的相位角。例如中国专利申请号201010212448.1、201210171339.9、201320598850.7、201320879275.8、201610380597.6等。尽管这些装置已经成熟地应用在发动机上，但是已经发现这些装置存在响应速度较慢、相位平稳性较差的问题，而且工作受油温，油压的影响。
在现有的电动相位调节装置中，相位调节多采用同向减速机构，即电机相对壳体的转动方向与相位调节方向一致。实际工作时，相位后调时阻力矩较前调时需求较小，同向相位调节装置达到预设调节速度时，需要电机的输出功率较大，造成调节装置的效率低。
发明内容
本发明的目的在于：针对上述存在的问题，提供一种不仅可减小轴向尺寸和重量，而且可提高工作效率的电动相位调节装置，减小电机功率的装置。
本发明的技术方案是这样实现的：一种电动相位调节装置，包括：电机和相位器，所述电机的电机轴的旋转运动经相位器减速后，控制发动机凸轮轴相对于曲轴的相位；所述相位器包括：壳体、从动齿轮、输出轮、支撑架和浮动盘；其特征在于：所述壳体与发动机曲轴同步旋转；所述从动齿轮设置于壳体内部，其从动齿部与壳体的驱动齿部相互啮合；所述输出轮设置于壳体内部，并与所述发动机凸轮轴刚性连接，且可绕壳体轴线旋转；所述浮动盘设置在从 动齿轮与输出轮之间，所述浮动盘可分别相对于从动齿轮和输出轮径向滑动，且所述从动齿轮、浮动盘和输出轮同步旋转；所述支撑架设置于壳体内部，可绕壳体轴线偏心旋转，且所述支撑架在径向支撑所述从动齿轮；所述电机轴驱动支撑架旋转时，所述从动齿轮围绕支撑架做行星运动，其自转通过浮动盘传递给输出轮。
本发明所述的电动相位调节装置，其所述壳体外部可通过链条或皮带与发动机曲轴同步旋转，其内部设置有腔体和驱动齿部，所述腔体形成内部环形支撑面，用于支撑所述输出轮，所述内部环形支撑面与驱动齿部轴向相邻，并与壳体的轴向重合。
本发明所述的电动相位调节装置，其所述壳体包括链轮、驱动齿圈和前盖板，所述链轮、驱动齿圈和前盖板通过连接件锁紧组合在一起；所述驱动齿圈内部形成驱动齿部，在所述链轮上设置有至少一个链轮限位凸台。
本发明所述的电动相位调节装置，其所述从动齿轮包括从动齿部和从动轴承，在所述从动齿轮一侧端面设置从动齿轮凸台，所述从动齿轮凸台与浮动盘配合，用于传递从动齿轮的旋转运动。
本发明所述的电动相位调节装置，其所述从动齿轮包括从动齿部和从动轴承，在所述从动齿轮一侧端面设置有从动齿轮槽口，所述从动齿轮槽口与浮动盘配合，用于传递从动齿轮的旋转运动。
本发明所述的电动相位调节装置，其所述输出轮一侧端面与发动机凸轮轴刚性连接在一起，且在该端面设置有至少一个输出轮限位凸台，所述输出轮的另一侧端面设置有输出轮凸台，所述输出轮凸台与浮动盘配合，用于接受来自从动齿轮的旋转运动。
本发明所述的电动相位调节装置，其所述输出轮一侧端面与发动机凸轮轴 刚性连接在一起，且在该端面设置有至少一个输出轮限位凸台，所述输出轮的另一侧端面设置有输出轮槽口，所述输出轮槽口与浮动盘配合，用于接受来自从动齿轮的旋转运动。
本发明所述的电动相位调节装置，其在所述输出轮与发动机凸轮轴连接的端面上设置有油道，在所述发动机凸轮轴上设置有与油道连通的凸轮轴油孔，在所述输出轮上设置有与油道连通的输出轮油孔，润滑油由凸轮轴油孔进入，流经油道，并通过输出轮油孔进入相位器。
本发明所述的电动相位调节装置，其所述壳体的链轮上的链轮限位凸台设置在输出轮限位凸台之间，所述相位器的可调角度由链轮限位凸台角度α和两个输出轮限位凸台之间角度β确定，当所述电机失效时，发动机仍可运转。
本发明所述的电动相位调节装置，其所述支撑架包括中心轴、支撑架轴承和偏心套，所述偏心套的内圆面与外圆面的轴心线彼此平行不重合，所述支撑架轴承设置在中心轴与偏心套之间，所述偏心套可相对于中心轴偏心旋转。
本发明所述的电动相位调节装置，其在所述浮动盘设有十字分布的槽口，分别可以与所述从动齿轮凸台和输出轮凸台间隙配合，且可径向自由滑动。
本发明所述的电动相位调节装置，其在所述浮动盘设有十字分布的分支，分别可以与所述从动齿轮槽口和输出轮槽口间隙配合，且可径向自由滑动。
本发明涉及使用电机和行星减速器，动态调节内燃机凸轮轴相对于曲轴的相位角，以调节发动机气门打开和关闭的时刻，实现提高内燃机燃油效率，采用本装置不仅可减小轴向尺寸和重量，而且可提高该相位调节装置的效率，同时，还可降低该相位调节装置的工作噪音，并延长使用寿命。
附图说明
图1是本发明的结构示意图。
图2是本发明的拆分示意图。
图3和图4是本发明中壳体的结构示意图。
图5和图6是本发明中从动齿轮的两种实施案例的结构示意图。
图7是本发明中输出轮油道的结构示意图。
图8和图9是本发明中输出轮的两种实施案例的结构示意图。
图10是本发明中支撑架的结构示意图。
图11和图12是本发明中浮动盘的两种实施案例的结构示意图。
图13是本发明中相位器可调角度确定的示意图。
图14是本发明齿轮啮合示意图。
附图标记：1为电机，2为相位器，3为发动机凸轮轴，4为电机轴，401为凸轮轴油孔，5为壳体，501为链轮，502为驱动齿圈，503为前盖板，504为腔体，505为驱动齿部，506为链轮限位凸台，6为从动齿轮，601为从动齿部，602为从动轴承，603为从动齿轮凸台，604为从动齿轮凸台平面，605为从动齿轮槽口，7为输出轮，701为输出轮限位凸台，702为输出轮凸台，703为输出轮凸台平面，704为油道，705为输出轮油孔，706为输出轮槽口，8为支撑架，801为中心轴，802为支撑架轴承，803为偏心套，9为浮动盘，901为浮动盘槽口，902为浮动盘槽口，903为浮动盘分支，904为浮动盘分支，11为中央螺栓。
具体实施方式
下面结合附图，对本发明作详细的说明。
为了使本发明的目的、技术方案及优点更加清楚明白，以下结合附图及实施例，对本发明进行进一步详细说明。应当理解，此处所描述的具体实施例仅仅用以解释本发明，并不用于限定本发明。
如图1和2所示，一种电动相位调节装置，包括电机1和相位器2，所述电 机1的电机轴4的旋转经相位器2减速后，控制发动机凸轮轴3相对于曲轴的相位，所述相位器2包括壳体5、从动齿轮6、输出轮7、支撑架8和浮动盘9，所述从动齿轮6设置于壳体5内部，所述从动齿轮6的从动齿部601与壳体5的驱动齿部505相互啮合，所述输出轮7设置于壳体5的腔体504内部且可绕壳体5轴线旋转，所述浮动盘9设置在从动齿轮6与输出轮7之间，所述浮动盘9可分别相对于从动齿轮6和输出轮7在径向上滑动，且所述从动齿轮6、浮动盘9和输出轮7同步转动，所述支撑架8设置于壳体5内部，所述支撑架8的中心轴801轴线与输出轮7轴线重合，并通过连接件螺钉11与输出轮7连接在一起，所述电机轴3驱动支撑架8旋转时，所述从动齿轮6围绕支撑架8做行星运动，其自转通过浮动盘9传递给输出轮7。
如图3和4所示，所述壳体5外部为链轮结构，其内部设置有腔体504和驱动齿部505，所述腔体504形成内部环形支撑面，所述内部环形支撑面与驱动齿部505轴向相邻且轴向重合，并与壳体5的轴向重合，在本实施例中，为了方便加工和装配，所述壳体5包括链轮501、驱动齿圈502和前盖板503，所述链轮501、驱动齿圈502和前盖板503通过连接件507锁紧组合在一起，所述链轮501外周形成链轮结构，所述驱动齿圈502内部形成驱动齿部505，在所述链轮501上设置有链轮限位凸台506。
如图5所示，所述从动齿轮6的其中一种实施案例：包括从动齿部601和从动轴承602，在所述从动齿轮6一侧端面设置有至少两个从动齿轮凸台603，所述从动齿轮凸台603与浮动盘9上的槽口配合，用于传递从动齿轮6的旋转运动，其中，所述从动齿轮凸台603为两个，且均匀的分布在从动齿轮6同一侧端面上，在本实施例中，为了方便从动齿轮凸台加工及提高精度，所述从动齿轮凸台603由销钉镶嵌在从动齿轮6端面部组成，为了防止销钉因接触应力 过大而变形，在所述从动齿轮凸台603上对称地加工为两个从动齿轮凸台平面604。
如图6所示，所述从动齿轮6的其中一种实施案例包括：从动齿部601和从动轴承602，在所述从动齿轮6一侧端面设置有至少两个从动齿轮槽口605，所述从动齿轮槽口605与浮动盘9配合，用于传递从动齿轮6的旋转运动。
如图8所示，所述输出轮7的其中一种实施案例：输出轮7一侧端面与发动机凸轮轴4刚性连接在一起，且在该端面设置有两个输出轮限位凸台701，所述输出轮7的另一侧端面设置有至少两个个输出轮凸台702，所述输出轮凸台702与浮动盘9上的槽口配合，用于接受来自从动齿轮6的扭矩，其中，所述输出轮凸台702为两个，且均匀分布在输出轮7同一侧端面上，为了方便输出轮凸台的加工，所述输出轮凸台702由销钉镶嵌在输出轮7端面部组成，为了防止销钉因接触应力过大而变形，在所述输出轮凸台702对称地加工为两个输出轮凸台平面703。
如图9所示，所述输出轮7的其中一种实施案例：输出轮7的另一种实施案例的特征在于：所述输出轮7一侧端面与发动机凸轮轴4刚性连接在一起，且在该端面设置有至少一个输出轮限位凸台701，所述输出轮7的另一侧端面设置有至少两个输出轮槽口706，所述输出轮槽口706与浮动盘9配合，用于接受来自从动齿轮6的旋转运动。
如图7所示，在本实施例中，为了使相位器得到有效润滑并减少发动机的机油消耗，在所述输出轮7与发动机凸轮轴4连接的端面上设置有油道704，在所述发动机凸轮轴4上设置有与油道704连通的凸轮轴油孔401，在所述输出轮7上设置有与油道704连通的输出轮油孔705，润滑油由凸轮轴油孔401进入，流经油道704，并通过输出轮油孔705进入相位器2。
如图13所示，所述链轮501上的链轮限位凸台506设置在两个输出轮限位凸台701之间，所述相位器2的可调角度由链轮限位凸台506角度α和两个输出轮限位凸台701之间角度β确定，当所述电机1失效时，发动机仍可运转。
如图10所示，所述支撑架8包括中心轴801、支撑架轴承802和偏心套803，所述偏心套803的内圆面与外圆面的轴心线彼此平行不重合，所述支撑架轴承802设置在中心轴801与偏心套803之间，所述偏心套803可相对于中心轴801偏心旋转。
如图11所示，在所述浮动盘9其中的一种实施案例包括：浮动盘9的外圆周设置有与从动齿轮6上设置的从动齿轮凸台603对应配合的两个从动齿轮槽口901，所述从动齿轮凸台603插入从动齿轮槽口901，在所述浮动盘9的内圆周上设置有与输出轮7上设置的输出轮凸台702对应配合的两个输出轮槽口902，所述输出轮凸台702插入输出轮槽口902，所述从动齿轮槽口901和输出轮槽口902在浮动盘9上呈十字状布置且均匀分布。
如图12所示，在所述浮动盘9其中的一种实施案例包括：浮动盘(9)设有十字分布的四个分支(903,904)，分别可以与所述从动齿轮槽口(605)和输出轮槽口(706)间隙配合，且可径向自由滑动。
以上所述仅为本发明的较佳实施例而已，并不用以限制本发明，凡在本发明的精神和原则之内所作的任何修改、等同替换和改进等，均应包含在本发明的保护范围之内。

Claims (12)

  1. 一种电动相位调节装置，包括：
    电机(1)和相位器(2)，所述电机(1)的电机轴(4)的旋转运动经相位器(2)减速后，控制发动机凸轮轴(3)相对于曲轴的相位；
    所述相位器(2)包括：壳体(5)、从动齿轮(6)、输出轮(7)、支撑架(8)和浮动盘(9)；其特征在于：所述壳体(5)与发动机曲轴同步旋转；所述从动齿轮(6)设置于壳体(5)内部，其从动齿部(601)与壳体(5)的驱动齿部(505)相互啮合；所述输出轮(7)设置于壳体(5)内部，并与所述发动机凸轮轴(3)刚性连接，且可绕壳体(5)轴线旋转；所述浮动盘(9)设置在从动齿轮(6)与输出轮(7)之间，所述浮动盘(9)可分别相对于从动齿轮(6)和输出轮(7)径向滑动，且所述从动齿轮(6)、浮动盘(9)和输出轮(7)同步旋转；所述支撑架(8)设置于壳体(5)内部，可绕壳体(5)轴线偏心旋转，且所述支撑架(8)在径向支撑所述从动齿轮(6)；所述电机轴(4)驱动支撑架(8)旋转时，所述从动齿轮(6)围绕支撑架(8)做行星运动，其自转通过浮动盘(9)传递给输出轮(7)。
  2. 根据权利要求1所述的电动相位调节装置，其特征在于：所述壳体(5)外部可通过链条或皮带与发动机曲轴同步旋转，其内部设置有腔体(504)和驱动齿部(505)，所述腔体(504)形成内部环形支撑面，用于支撑所述输出轮(7)，所述内部环形支撑面与驱动齿部(505)轴向相邻，并与壳体(5)的轴向重合。
  3. 根据权利要求2所述的电动相位调节装置，其特征在于：所述壳体(5)包括链轮(501)、驱动齿圈(502)和前盖板(503)，所述链轮(501)、驱动齿圈(502)和前盖板(503)通过连接件(507)锁紧组合在一起；所述驱动齿圈(502)内部形成驱动齿部(505)，在所述链轮(501)上设置有至少一个 链轮限位凸台(506)。
  4. 根据权利要求1所述的电动相位调节装置，其特征在于：所述从动齿轮(6)包括从动齿部(601)和从动轴承(602)，在所述从动齿轮(6)一侧端面设置从动齿轮凸台(603)，所述从动齿轮凸台(603)与浮动盘(9)配合，用于传递从动齿轮(6)的旋转运动。
  5. 根据权利要求1所述的电动相位调节装置，其特征在于：所述从动齿轮(6)包括从动齿部(601)和从动轴承(602)，在所述从动齿轮(6)一侧端面设置有从动齿轮槽口(605)，所述从动齿轮槽口(605)与浮动盘(9)配合，用于传递从动齿轮(6)的旋转运动。
  6. 根据权利要求1所述的电动相位调节装置，其特征在于：所述输出轮(7)一侧端面与发动机凸轮轴(3)刚性连接在一起，且在该端面设置有至少一个输出轮限位凸台(701)，所述输出轮(7)的另一侧端面设置有输出轮凸台(702)，所述输出轮凸台(702)与浮动盘(9)配合，用于接受来自从动齿轮(6)的旋转运动。
  7. 根据权利要求1所述的电动相位调节装置，其特征在于：所述输出轮(7)一侧端面与发动机凸轮轴(3)刚性连接在一起，且在该端面设置有至少一个输出轮限位凸台(701)，所述输出轮(7)的另一侧端面设置有输出轮槽口(706)，所述输出轮槽口(706)与浮动盘(9)配合，用于接受来自从动齿轮(6)的旋转运动。
  8. 根据权利要求6或7所述的电动相位调节装置，其特征在于：在所述输出轮(7)与发动机凸轮轴(3)连接的端面上设置有油道(704)，在所述发动机凸轮轴(3)上设置有与油道(704)连通的凸轮轴油孔(401)，在所述输出轮(7)上设置有与油道(704)连通的输出轮油孔(705)，润滑油由凸轮轴油 孔(401)进入，流经油道(704)，并通过输出轮油孔(705)进入相位器(2)。
  9. 根据权利要求8所述的电动相位调节装置，其特征在于：所述壳体(5)的链轮(501)上的链轮限位凸台(506)设置在输出轮限位凸台(701)之间，所述相位器(2)的可调角度由链轮限位凸台(506)角度α和两个输出轮限位凸台(701)之间角度β确定，当所述电机(1)失效时，发动机仍可运转。
  10. 根据权利要求1所述的电动相位调节装置，其特征在于：所述支撑架(8)包括中心轴(801)、支撑架轴承(802)和偏心套(803)，所述偏心套(803)的内圆面与外圆面的轴心线彼此平行不重合，所述支撑架轴承(802)设置在中心轴(801)与偏心套(803)之间，所述偏心套(803)可相对于中心轴(801)偏心旋转。
  11. 根据权利要求4或6所述的电动相位调节装置，其特征在于：在所述浮动盘(9)设有十字分布的槽口(901,902)，分别可以与所述从动齿轮凸台(603)和输出轮凸台(702)间隙配合，且可径向自由滑动。
  12. 根据权利要求5或7所述的电动相位调节装置，其特征在于：在所述浮动盘(9)设有十字分布的分支(903,904)，分别可以与所述从动齿轮槽口(605)和输出轮槽口(706)间隙配合，且可径向自由滑动。
PCT/CN2018/092318 2018-06-22 2018-06-22 一种电动相位调节装置 WO2019241984A1 (zh)

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US20030226532A1 (en) * 2002-04-19 2003-12-11 Nippon Soken, Inc. Valve timing adjusting device
US20100180845A1 (en) * 2009-01-21 2010-07-22 Denso Corporation Valve timing controller
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