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WO2006116919A1 - Mecanisme de transmission a engrenage - Google Patents

Mecanisme de transmission a engrenage Download PDF

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Publication number
WO2006116919A1
WO2006116919A1 PCT/CN2006/000814 CN2006000814W WO2006116919A1 WO 2006116919 A1 WO2006116919 A1 WO 2006116919A1 CN 2006000814 W CN2006000814 W CN 2006000814W WO 2006116919 A1 WO2006116919 A1 WO 2006116919A1
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WO
WIPO (PCT)
Prior art keywords
gear
driven
gears
driving
teeth
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2006/000814
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English (en)
French (fr)
Inventor
Risi Na
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Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of WO2006116919A1 publication Critical patent/WO2006116919A1/zh
Priority to US11/934,841 priority Critical patent/US7836785B2/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/24—Toothed gearings for conveying rotary motion without gears having orbital motion involving gears essentially having intermeshing elements other than involute or cycloidal teeth
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19023—Plural power paths to and/or from gearing
    • Y10T74/19074—Single drive plural driven
    • Y10T74/19079—Parallel
    • Y10T74/19084—Spur
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19642—Directly cooperating gears
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19642—Directly cooperating gears
    • Y10T74/19647—Parallel axes or shafts
    • Y10T74/19651—External type
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19642—Directly cooperating gears
    • Y10T74/19679—Spur
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19949—Teeth
    • Y10T74/19963—Spur

Definitions

  • the present invention relates to a power machine, and more particularly to a gear transmission mechanism. Background of the invention
  • the energy of the drive gear to the driven gear is substantially equal to the energy produced by the drive gear in the event of very low energy losses.
  • the energy of the drive gear to each driven gear is substantially evenly distributed in the case of very low energy losses, ie in the case of one-to-two.
  • the energy of the driving gear to each of the driven gears is about half of the energy generated by the driving gears. In the case of a pair of three, the energy of the driving gears to each of the driven gears is about 1/3 of the energy generated by the driving gears.
  • the pitch of the driving gear and the pitch of the driven gear are generally equal, that is, one tooth of the driving gear meshes with one tooth of the driven gear.
  • Figure 1 is a schematic diagram of the current gear transmission mechanism.
  • the right driving gear rotates counterclockwise under the action of external power
  • the left driven gear rotates clockwise under the driving of the driving gear, and energy is transmitted from the driving gear to the driven gear.
  • a gear transmission mechanism comprising a driving gear and at least two driven gears, characterized in that the number of driving gear teeth and the driven gear that can be accommodated between adjacent teeth of each driven gear during operation The number of the gears is the same, and the engagement of the driving gear with each of the driven gears is performed one by one in sequence.
  • the driving gear and the driven gear are helical gears.
  • the driven gears are evenly distributed with respect to the drive gear.
  • the number of the driven gears is two, and the two driven gears are symmetrically distributed with respect to the driving gears.
  • the number of the driven gears is two, and the teeth of the two driving gears can be accommodated between adjacent teeth of each driven gear.
  • the gear transmission mechanism provided by the present invention has the following beneficial effects:
  • the pitch of the driven gear is increased, the pitch of the driven gear is increased to 2 times or more of the pitch of the driving gear, and the driving gear and the plurality of slaves are changed in the case of a master and a slave.
  • the meshing relationship between the moving gears causes the driving gear to be in a non-engaged state with the other driven gears when one of the gear teeth of the driving gear is engaged with one of the gear teeth of the driven gear, the driving gear and the plurality of driven gears
  • the one-to-one transmission is alternately performed. Therefore, the gear transmission mechanism provided by the present invention effectively reduces the number of driven gear teeth, thereby simplifying the manufacturing process of the driven gear and greatly reducing the manufacturing cost of the driven gear. The purpose of saving the manufacturing cost of the driven gear.
  • Figure 1 is a schematic view of the current gear transmission mechanism
  • FIG. 2 is a schematic view of a gear transmission mechanism in accordance with an embodiment of the present invention. Mode for carrying out the invention
  • the core idea of the invention is: by increasing the pitch of the driven gear, the pitch of the driven gear is increased to 2 times or more of the pitch of the driving gear, and the initiative is changed in the case of a master multi-slave
  • the meshing relationship between the gear and the plurality of driven gears causes the driving gear to be in a non-engaged state with the other driven gear when one of the gear teeth of the driving gear is engaged with one of the driven gears, the driving gear and the driving gear
  • Each of the driven gears is driven one by one in sequence, and the engagement of the driving gears with the driven gears is performed one by one in sequence.
  • the pitch of the driven gear is increased, so that the pitch of the driven gear is generally twice or three times the pitch of the driving gear, which can greatly simplify the driven gear.
  • the manufacturing process reduces the manufacturing cost of the driven gear.
  • the engagement of the driving gears with the respective driven gears is performed one by one in sequence.
  • the pitch of the driven gear is determined by the number of driven gears. If a driving gear drives two driven gears, the pitch of the driven gear is twice the pitch of the driving gear, that is, each tooth of the driven gear can mesh with the two teeth of the driving gear; The driving gear drives the three driven gears, and the pitch of the driven gear is three times the pitch of the driving gear, that is, each tooth of the driven gear can mesh with the three teeth of the driving gear.
  • the engagement of the driving gears with the driven gears is sequentially performed one by one, and at the time of installation, the driving gear and the first driven teeth are arranged one by one.
  • the driving gear and the second driven gear are in a state of being disengaged.
  • the driving gear is engaged with the first driven gear that is in the immediately engaged state, the driving gear is in a non-engaged state with the second driven gear that is previously in the disengaged state.
  • the driving gear will mesh with the second driven gear while being disengaged from the first driven gear. In this way, the gear transmission of one belt and two becomes a one-to-one gear transmission instantaneously.
  • one driving gear drives three driven gears
  • the driving gear and the second driven gear and the third driven gear are in a state of being disengaged.
  • the driving gear is engaged with the first driven gear which is in the immediately engaged state
  • the driving gear is in a non-engaged state with the second driven gear and the third driven gear which are in the immediately disengaged state.
  • the driving gear will mesh with the second driven gear while being disengaged from the first driven gear.
  • the main gear meshes with the third driven gear while being disengaged from the second driven gear.
  • the gear transmission of the belt and the belt becomes a gear transmission of one belt and one.
  • the generally selected gear is a helical gear, and each driven gear is generally evenly distributed with respect to the driving gear.
  • the two driven gears are generally symmetrically distributed with respect to the driving gear.
  • FIG. 2 is a schematic illustration of a gear transmission mechanism in accordance with an embodiment of the present invention.
  • one driving gear drives the two driven gears.
  • 1 is the driving gear
  • 2 and 3 are the driven gears
  • the pitch of the driven gears 2 and 3 is twice the pitch of the driving gear, and the two teeth of the driving gear 1 can be accommodated during the meshing.
  • the direction of the helix angle of the driven gear 2 and the 3 teeth is the same, and the direction of the helix angle of the pinion of the drive gear 1 is opposite to the direction of the helix of the driven gear 2 and 3 teeth. in contrast.
  • the driven gear 3 is One of the teeth and one of the teeth of the driving gear 1 are in a state of being about to disengage.
  • the gear transmission mechanism provided by the invention can reduce the number of teeth of the driven gear by increasing the tooth pitch of the driven gear, thereby simplifying the manufacturing process of the driven gear and saving the manufacturing cost of the driven gear.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear Transmission (AREA)
  • Electrophotography Configuration And Component (AREA)

Description

一种齿轮传动机构 技术领域
本发明涉及动力机械， 尤其涉及一种齿轮传动机构。 发明背景
在动力机械中， 多轴的旋转， 速度的改变， 在很多情况下都是通过 齿轮传动实现的。 对于一对一的一级传动而言， 在能量损耗非常小的情 况下， 主动齿轮传动到从动齿轮的能量基本与主动齿轮产生的能量相 当。 而对于一对二或一对三的一级传动而言， 在能量损耗非常小的情况 下， 主动齿轮传动到每个从动齿轮的能量基本是均匀分配的， 即在一对 二的情况下主动齿轮传动到每个从动齿轮的能量约为主动齿轮产生能 量的一半， 在一对三的情况下主动齿轮传动到每个从动齿轮的能量约为 主动齿轮产生能量的 1/3。
在目前的齿轮传动机构中， 主动齿轮的齿距与从动齿轮的齿距一般 都是相等的， 即主动齿轮的一个轮齿啮合从动齿轮的一个轮齿。 如图 1 所示， 图 1为目前齿轮传动机构的示意图。 在图 1中， 右边的主动齿轮 在外部动力的作用下沿逆时针方向转动, 左边的从动齿轮在主动齿轮的 带动下沿顺时针方向转动， 能量从主动齿轮传送给从动齿轮。
由图 1可以看出， 由于主动齿轮的一个轮齿啮合从动齿轮的一个轮 齿，所以在主动齿轮齿距确定的情况下，从动齿轮的齿距也就被确定了。 如果主动齿轮齿距很小， 则从动齿轮轮齿的数量将会很大, 导致从动齿 轮的制造工艺复杂， 制造成本很高。 发明内容
有鉴于此， 本发明的主要目的在于提供一种齿轮传动机构， 以简化 从动齿轮的制造工艺， 节约从动齿轮的制造成本。
为达到上述目的， 本发明的技术方案是这样实现的：
一种齿轮传动机构， 包括一个主动齿轮和至少两个从动齿轮， 其特 征在于， 在运行时每个从动齿轮相邻轮齿之间可容纳的主动齿轮轮齿的 个数与从动齿轮的个数相同， 且主动齿轮与每个从动齿轮的啮合依顺序 逐个进行。
所述主动齿轮和从动齿轮为斜齿齿轮。
所述各从动齿轮相对于主动齿轮均匀分布。
所述从动齿轮的个数为 2, 所述两个从动齿轮相对于主动齿轮呈对 称分布。
所述从动齿轮的个数为 2, 每个从动齿轮相邻轮齿之间可容纳 2个 主动齿轮的轮齿。
从上述技术方案可以看出， 本发明提供的齿轮传动机构具有以下有 益效果：
由于增大了从动齿轮的轮齿间距， 将从动齿轮的齿距增大为主动齿 轮齿距的 2倍或 2倍以上， 并在一主多从的情况下改变主动齿轮与多个 从动齿轮之间的啮合关系， 使主动齿轮的一个轮齿在与从动齿轮的某一 个轮齿处于啮合状态时， 主动齿轮与其他从动齿轮处于非啮合状态， 主 动齿轮与多个从动齿轮交替进行一带一的传动， 所以， 本发明提供的齿 轮传动机构有效地减少了从动齿轮轮齿的数量, 进而简化了从动齿轮的 制造工艺， 并大大降低了从动齿轮的制造成本， 达到了节约从动齿轮制 造成本的目的。 附图简要说明
图 1为目前齿轮传动机构的示意图；
图 2为依照本发明实施例齿轮传动机构的示意图。 实施本发明的方式
为使本发明提供的技术方案更加清楚明白， 以下结合具体的实施例 对本发明进一步详细说明。
本发明的核心思想是： 通过增大从动齿轮的齿距， 将从动齿轮的齿 距增大为主动齿轮齿距的 2倍或 2倍以上， 并在一主多从的情况下改变 主动齿轮与多个从动齿轮之间的啮合关系, 使主动齿轮的一个轮齿在与 从动齿轮的某一个轮齿处于啮合状态时， 主动齿轮与其他从动齿轮处于 非啮合状态， 主动齿轮与各个从动齿轮依顺序进行一带一的传动, 实现 主动齿轮对从动齿轮的啮合依顺序逐个进行。
对于一个主动齿轮带动一个从动齿轮的情况而言, 增大从动齿轮的 齿距， 使从动齿轮的齿距一般为主动齿轮齿距的 2倍或 3倍， 可以大大 简化从动齿轮的制造工艺， 降低从动齿轮的制造成本。
对于一个主动齿轮带动多个从动齿轮的情况而言, 作为本发明的优 选实施例，主动齿轮对各从动齿轮的啮合依顺序逐个进行。一般情况下， 从动齿轮的齿距由从动齿轮的个数决定。 如果是一个主动齿轮带动两个 从动齿轮， 则从动齿轮的齿距为主动齿轮齿距的 2倍， 即从动齿轮的每 个轮齿可以啮合主动齿轮的 2个轮齿; 如果是一个主动齿轮带动三个从 动齿轮， 则从动齿轮的齿距为主动齿轮齿距的 3倍， 即从动齿轮的每个 轮齿可以啮合主动齿轮的 3个轮齿。
在一个主动齿轮带动两个从动齿轮的情况下, 为实现主动齿轮对各 从动齿轮的啮合依顺序逐个进行, 在安装时， 在主动齿轮与第一从动齿 轮处于即将进入啮合状态时， 主动齿轮与第二从动齿轮处于即将脱离啮 合状态。 在主动齿轮与在先处于即将进入啮合状态的第一从动齿轮处于 啮合状态时， 主动齿轮与在先处于即将脱离啮合状态的第二从动齿轮处 于非啮合状态。 然后， 由于旋转惯性的存在， 在旋转惯性力的作用下， 主动齿轮便会与第二从动齿轮进行啮合， 同时脱离与第一从动齿轮的啮 合。 这样一来， 一带二的齿轮传动瞬时就变成了一带一的齿轮传动。
在一个主动齿轮带动三个从动齿轮的情况下， 为实现主动齿轮对各 从动齿轮的啮合依顺序逐个进行， 在安装时， 在主动齿轮与第一从动齿 轮处于即将进入啮合状态时， 主动齿轮与第二从动齿轮和第三从动齿轮 处于即将脱离啮合状态。 在主动齿轮与在先处于即将进入啮合状态的第 一从动齿轮处于啮合状态时， 主动齿轮与在先处于即将脱离啮合状态的 第二从动齿轮和第三从动齿轮处于非啮合状态。 然后， 由于旋转惯性的 存在，在旋转惯性力的作用下，主动齿轮便会与第二从动齿轮进行啮合， 同时脱离与第一从动齿轮的啮合。 然后， 再在旋转惯性力的作用下， 主 动齿轮与第三从动齿轮进行啮合， 同时脱离与第二从动齿轮的啮合。 这 样一来， 一带三的齿轮传动瞬时也就变成了一带一的齿轮传动。
一个主动齿轮带动三个以上从动齿轮的情况与一个主动齿轮带动两 个从动齿轮或三个从动齿轮的情况类似， 这里就不再赘述。
另外， 考虑到齿轮传动机构在传动中的平稳性和连续性， 在本发明 提供的齿轮传动机构中， 一般选用的齿轮为斜齿齿轮， 并且各从动齿轮 一般相对于主动齿轮均匀分布。 较佳地， 对于一个主动齿轮带动两个从 动齿轮的情况， 两个从动齿轮一般相对于主动齿轮呈对称分布。 实施例 1
如图 2所示， 图 2为依照本发明实施例齿轮传动机构的示意图。 在 本实施例中， 一个主动齿轮带动两个从动齿轮。 其中， 1为主动齿轮， 2 和 3为从动齿轮， 从动齿轮 2和 3的齿距为主动齿轮齿距的 2倍， 在啮 合时可以包容主动齿轮 1的两个轮齿。
在装配时为保证有良好的啮合， 从动齿轮 2和 3轮齿螺旋角的旋向 相同， 主动齿轮 1轮齿螺旋角的旋向则与从动齿轮 2和 3轮齿螺旋角的 旋向相反。 在安装时为保证主动齿轮对从动齿轮的啮合交替逐个进行， 对照图 2, 在主动齿轮 1的一个轮齿与从动齿轮 2的一个轮齿即将进入 啮合状态时，从动齿轮 3的某一个轮齿与主动齿轮 1 的一个轮齿处于即 将脱离的状态。 在主动齿轮 1的一个轮齿与从动齿轮 2的一个轮齿处于 啮合状态时，从动齿轮 3的某一个轮齿与主动齿轮 1 的一个轮齿处于非 啮合的状态。 然后， 由于旋转惯性的存在， 主动齿轮 1的一个轮齿与从 动齿轮 2的一个轮齿脱离啮合状态, 从动齿轮 3的某一个轮齿与主动齿 轮 1 的一个轮齿进入啮合状态。 如是， 整个齿轮传动机构启动后， 整个 的一带二的齿轮传动， 就依顺序进行瞬时一带一的传动。 工业适用性
本发明提供的齿轮传动机构， 由于增大了从动齿轮的轮齿间距， 可 以减少从动齿轮的轮齿数量， 进而简化了从动齿轮的制造工艺， 节约了 从动齿轮的制造成本。

Claims

权 利 要 求 书
1、 一种齿轮传动机构， 包括一个主动齿轮和至少两个从动齿轮， 其 特征在于， 在运行时每个从动齿轮相邻轮齿之间可容纳的主动齿轮轮齿 的个数与从动齿轮的个数相同， 且主动齿轮与每个从动齿轮的啮合依顺 序逐个进行。
2、 '根据杈利要求 1所述的齿轮传动机构， 其特征在于， 所述主动齿 轮和从动齿轮为斜齿齿轮。
3、根据权利要求 1所述的齿轮传动机构， 其特征在于， 所述各从动 齿轮相对于主动齿轮均匀分布。
4、根据杈利要求 3所述的齿轮传动机构， 其特征在于， 所述从动齿 轮的个数为 2, 所述两个从动齿轮相对于主动齿轮呈对称分布。
5、根据权利要求 1所述的齿轮传动机构， 其特征在于， 所述从动齿 轮的个数为 2,每个从动齿轮相邻轮齿之间可容纳 2个主动齿轮的轮齿。
PCT/CN2006/000814 2005-05-05 2006-04-27 Mecanisme de transmission a engrenage Ceased WO2006116919A1 (fr)

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KR20160022646A (ko) * 2014-08-20 2016-03-02 삼성전자주식회사 동력전달장치

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4062250A (en) * 1975-09-16 1977-12-13 Elmeg Elektro-Mechanik Gmbh Gear train for interconnecting side-by-side positioned drums, rolls, wheels, etc.
EP0841230A1 (en) * 1995-04-28 1998-05-13 United Technologies Motor Systems, Inc. Multi-functional apparatus employing an intermittent motion mechanism
CN2358274Y (zh) * 1998-09-10 2000-01-12 上海市浦东电工厂 齿轮式间歇运动装置
CN1307217A (zh) * 2000-01-31 2001-08-08 株式会社三协精机制作所 电动机式风门装置
CN1603665A (zh) * 2003-09-03 2005-04-06 株式会社恩普乐 塑料铸造的齿轮以及用此齿轮的间歇旋转传动装置和齿轮组

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1016545A (en) * 1909-09-01 1912-02-06 Cyrus C Bultman Mechanical movement.
US4567783A (en) * 1983-02-14 1986-02-04 Ex-Cell-O Corporation Multi-angle pinion and gear power transmission

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4062250A (en) * 1975-09-16 1977-12-13 Elmeg Elektro-Mechanik Gmbh Gear train for interconnecting side-by-side positioned drums, rolls, wheels, etc.
EP0841230A1 (en) * 1995-04-28 1998-05-13 United Technologies Motor Systems, Inc. Multi-functional apparatus employing an intermittent motion mechanism
CN2358274Y (zh) * 1998-09-10 2000-01-12 上海市浦东电工厂 齿轮式间歇运动装置
CN1307217A (zh) * 2000-01-31 2001-08-08 株式会社三协精机制作所 电动机式风门装置
CN1603665A (zh) * 2003-09-03 2005-04-06 株式会社恩普乐 塑料铸造的齿轮以及用此齿轮的间歇旋转传动装置和齿轮组

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