WO2017211175A1 - 蜗轮蜗杆机构 - Google Patents

蜗轮蜗杆机构 Download PDF

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Publication number
WO2017211175A1
WO2017211175A1 PCT/CN2017/085401 CN2017085401W WO2017211175A1 WO 2017211175 A1 WO2017211175 A1 WO 2017211175A1 CN 2017085401 W CN2017085401 W CN 2017085401W WO 2017211175 A1 WO2017211175 A1 WO 2017211175A1
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WIPO (PCT)
Prior art keywords
worm
axial
gear mechanism
limit position
worm gear
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PCT/CN2017/085401
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English (en)
French (fr)
Inventor
褚晓兵
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舍弗勒技术股份两合公司
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Publication of WO2017211175A1 publication Critical patent/WO2017211175A1/zh

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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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • 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
    • F16H57/00—General details of gearing
    • F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere

Definitions

  • the present invention relates to the field of worm gears, and in particular to a worm gear mechanism capable of adjusting the axial tooth gap of a worm wheel and a worm.
  • the worm gear mechanism includes a worm wheel 10 and a worm 20 that mesh with each other, the drive gear 30 is located on one axial side of the worm 20 and the worm gear 20 and the drive gear The 30 is fixedly coupled or formed integrally to form an assembly that is rotatable on the rotating shaft 40.
  • the worm gear mechanism further includes a retaining ring 50 mounted on the rotating shaft 40 and located on one axial side (the left side in the drawing) of the driving gear 30 and the other axial side (the right side in the drawing) of the worm 20, respectively.
  • the retaining ring 50, 60 serves as a stop for the worm 20 and the drive gear 30 in the axial direction A.
  • the retaining ring 50 abuts against the axial end surface of the drive gear 30, and the retaining ring 60 abuts against the axially opposite end surface of the worm 20 such that the worm 20 and the drive gear 30 are on the rotating shaft 40. There is no axial movement relative to the worm gear 10.
  • the present invention has been made based on the above-described drawbacks in the prior art. To this end, the present invention adopts the following technical solutions.
  • the present invention provides a worm gear mechanism including a worm gear and a worm meshed with each other, the worm being capable of being positioned between a first axial limit position and a second axial limit position relative to the worm gear Moving axially, and when the worm is in the first axial limit position, the worm rotates about a first rotational direction, the first active surface of the tooth portion of the worm abutting against the teeth of the worm gear a first active surface; when the worm is in the second axial limit position, the worm rotates in a second rotational direction, and the second active surface of the tooth portion of the worm abuts against the tooth portion of the worm gear Second action surface.
  • the worm gear mechanism further includes: a driving member capable of driving the worm to move axially; and/or a limiting structure capable of limiting the worm to the first An axial limit position and the second axial limit position.
  • the drive members have different directions of rotation, and the worm is axially moved by changing the direction of rotation of the drive member.
  • the driving member is a driving gear
  • the driving gear also serves as a driving source for driving the worm to rotate.
  • the limiting structure comprises two stoppers respectively disposed on two axial sides of the worm, and a stopping surface of one of the two stoppers can define the worm In the first axial limit position, a stop face of the other of the two stops can define the worm in the second axial limit position.
  • the one stop is capable of driving the worm to move axially.
  • the worm is in a state where the worm is in the first axial limit position a gap between the stop faces of the other stopper is less than or equal to an axis between the second acting surface of the tooth portion of the worm and the second acting surface of the tooth portion of the worm wheel in the state To the tooth gap; and/or when the worm is in the second axial limit position, the gap between the worm and the stop surface of the one stop is less than or equal to the state in the state An axial tooth gap between the first acting surface of the tooth portion of the worm and the first acting surface of the tooth portion of the worm wheel.
  • the worm is formed with a worm thread portion at a portion close to the driving member, and the driving member has a driving member threaded portion for engaging with the worm thread portion, the driving member being engaged with each other
  • the relative rotation of the worm threaded portion and the threaded portion of the drive member drives the worm to move axially.
  • the worm gear mechanism further includes a rotating shaft that is mounted to the rotating shaft in a manner movable along the axial direction relative to the worm wheel on the rotating shaft.
  • the limiting structure is a latch structure or a latch structure.
  • the present invention provides a worm gear mechanism capable of adjusting the axial tooth gap of the worm gear when the rotation direction of the worm is changed, which can greatly reduce the wear of the worm gear mechanism.
  • Fig. 1a is a perspective view showing a prior art worm gear mechanism
  • Fig. 1b is a front elevational view showing a prior art worm gear mechanism.
  • Figure 2a is a schematic perspective view showing a worm gear mechanism according to the present invention
  • Figure 2b is a front elevational view showing the worm gear mechanism according to the present invention.
  • Figure 3a is a schematic view showing the meshing state of the worm gear according to the present invention when the worm is in the first axial limit position
  • Figure 3b is a view showing the worm gear according to the present invention when the worm is in the second axial limit position Schematic diagram of the meshing state.
  • the mark A indicates “axial direction", that is, the direction along the central axis of the worm; in addition, unless otherwise specified, “axial side” refers to the left side in the drawing, “the other side of the axis” Refer to the right side of the figure.
  • the “axial tooth gap L” refers to a gap in which the adjacent teeth of the worm wheel and the worm are engaged in the above-described axial direction; and the “gap" or “interval” referred to in the present invention means A gap or space in the above axial direction.
  • the worm gear mechanism includes a worm wheel 1, a worm 2, a drive gear 3, a rotating shaft 4, and two retaining rings 5, 6.
  • the worm wheel 1 and the worm 2 are meshed with each other, and the drive gear 3 serving as a driving member is located on one axial side of the worm 2.
  • the worm 2 and the drive gear 3 are separate components (no connection between each other) and the worm 2 is movable relative to the worm wheel 1 in the axial direction A to the first axial limit position and the second axial direction. Extreme position.
  • the drive gear 3 is provided with a center mounting hole
  • the worm 2 is provided with a center through hole extending along the center axis thereof and penetrating the entire worm 2.
  • the rotary shaft 4 passes through the center mounting hole of the drive gear 3 and the center through hole of the worm 2, respectively, so that the drive gear 3 and the worm 2 are mounted to the rotary shaft 4.
  • the drive gear 3 can not only drive the worm 2 to rotate about the rotating shaft 4, but also drive the worm 2 to move relative to the worm wheel 1 (drive gear 3) along the axial direction A.
  • this embodiment is only a simple and cost-effective implementation.
  • the worm 2 can alternatively be realized along the shaft by an additional drive structure. Move to A without turning.
  • the worm gear mechanism further includes the retaining rings 5, 6 mounted on the rotating shaft 4 and located on the axial side of the drive gear 3 and the other axial side of the worm 2, respectively, such that the drive gear 3 and The worm 2 is located between the retaining rings 5, 6 in the axial direction A.
  • Both of the retaining rings 5, 6 are not movable along the axial direction on the rotating shaft 4.
  • the retaining ring 5 is mounted on the rotating shaft 4 and always abuts against the axial end surface of the driving gear 3; the retaining ring 6 is also mounted on the rotating shaft 4, but in the case where the driving gear 3 drives the worm 2 to rotate in different directions
  • the retaining ring 6 has a different relative state to the worm 2 (described in detail below).
  • the drive gear 3 serves as a stopper on one axial side of the worm 2, and the first axial limit position of the worm 2 is defined by the end surface (stop surface) of the other side of the drive gear 3 in the axial direction.
  • the retaining ring 6 serves as a stop on the other axial side of the worm 2, and the second axial limit position of the worm 2 is defined by the axial one end face (stop face) of the retaining ring 6.
  • the worm 2 can be moved to the first axial limit position and the second axial limit position, respectively, so that the worm gear can be adjusted when the worm 2 is in different rotational directions.
  • the worm 2 is formed with an internal thread portion 21 at one axial side, that is, on the axial side of the center through hole of the worm 2.
  • An internal thread portion 21 is provided on the circumferential surface. Accordingly, the end surface of the other side of the drive gear 3 is provided with an external thread portion 31 for engaging with the internal thread portion 21, and the external thread portion 31 is provided to protrude from the end surface on the other side in the axial direction of the drive gear 3. And projecting into the protrusion in the center through hole of the worm 2.
  • the length of the male screw portion 31 in the axial direction A is larger than the length of the female screw portion 21 in the axial direction A.
  • the driving gear 3 can drive the worm 2 to move relative to the worm wheel 1 along the axial direction A by the internal thread portion 21 and the external thread portion 31 that mesh with each other, thereby driving the worm 2 to rotate about the rotating shaft 4, the specific process in the following content. Detailed description.
  • the worm 2 when the worm 2 is in the first axial limit position, the worm 2 abuts against the drive gear 3, and the teeth of the worm wheel 1 are on the other side of the axial direction and the teeth of the worm 2 are The first acting faces on one axial side abut each other.
  • the second acting surface of the tooth of the worm wheel 1 on one side in the axial direction and the second acting surface of the tooth of the worm 2 on the other side of the axial direction have an axial tooth gap L, on the other side of the axial direction of the worm 2
  • the end face has a gap D with the axial end face (stop face) of the retaining ring 6 such that the gap D is equal to the axial tooth gap L.
  • the worm 2 when the worm 2 is in the second axial limit position, the worm 2 abuts against the retaining ring 6, and the second acting surface of the teeth of the worm wheel 1 and the second acting surface of the teeth of the worm 2 abut each other. Pick up.
  • the first acting surface of the teeth of the worm wheel 1 and the first acting surface of the teeth of the worm 2 have an axial tooth gap L, and the end surface (stop surface) on the other side in the axial direction of the driving gear 3 and the worm 2
  • There is a gap D between the end faces on one axial side such that the gap D is equal to the axial tooth gap L.
  • the predetermined distance (equal to the gap D) of the worm 2 that can move relative to the worm wheel 1 along the axial direction A is equal to the axial tooth gap L, thereby buffering the change in the direction of rotation of the worm 2.
  • a violent collision between the worm wheel 1 and the worm 2 occurs.
  • the gap D may be made smaller than the axial gap L.
  • the drive gear 3 in a state where the drive gear 3 is always kept rotated in one direction, the drive gear 3 abuts against the worm 2 and is formed integrally as to rotate about the rotary shaft 4.
  • the worm wheel 2 In this state, the worm wheel 2 is in the first axial limit position and the first acting surface of the teeth of the worm wheel 1 abuts against the first acting surface of the teeth of the worm 2, the gap D being located between the worm 2 and the retaining ring 6. In this state, the worm wheel 1 rotates clockwise.
  • the drive gear 3 rotates from one direction to the other, the drive gear 3 A relative rotation occurs between the external thread portion 31 and the internal thread portion 21 of the worm 2, so that the worm 2 moves in the axial direction A with respect to the worm wheel 1 on the other side in the axial direction.
  • the gap between the drive gear 3 and the worm 2 is increased, and the gap between the worm 2 and the retaining ring 6 is reduced.
  • the worm 2 is moved to a state in contact with the retaining ring 6, at which time the worm wheel 2 is in the second axial limit position and the second acting surface of the teeth of the worm wheel 1 and the second acting surface of the teeth of the worm 2 abut each other. .
  • the drive gear 3 is employed as the drive member in the above specific embodiment, the present invention is not limited thereto.
  • the drive member is not limited to the drive gear 3, but other components or structures may be employed as long as the member and structure are capable of driving the worm 2 to move relative to the worm wheel 1 along the axial direction A.
  • a drive structure that simply drives the worm 2 to move relative to the worm wheel 1 along the axial direction A is provided.
  • first axial limit position is defined using the drive gear 3 in the above detailed description, the invention is not limited thereto. It is also possible to arrange the drive gear 3 on the outside of the retaining rings 5, 6, and then to define the first axial limit position and the second axial limit of the worm 2 by the retaining rings 5, 6, respectively. position.
  • the latch structure can define the worm 2 in a first axial extreme position and a second axial extreme position by providing a pin on the shaft 4.
  • the drive gear 3 may be limited to the rotary shaft 4 by the retaining ring 5, so that the drive gear 3 cannot move on the rotary shaft 4 in the axial direction A.
  • the drive gear 3 may be separately mounted to the rotating shaft 4 to omit the above-described retaining ring 5.
  • the axial interdental gap L is usually 0.05 mm to 0.10 mm, and thus the above-described gap D is preferably set to be less than or equal to 0.05 mm.
  • the drive gear 3 is immovable in the axial direction A.
  • the male screw portion 31 is formed on the drive gear 3, and the female screw portion 21 is formed on the worm 2.
  • the present invention is not limited thereto, and an external thread portion may be formed at an end portion on the axial side of the worm 2, and an internal thread portion may be correspondingly formed on the drive gear 3.
  • first active surface and the second active surface of the teeth of the worm wheel 1 refer to the axial direction of each of the plurality of teeth (tooth portions) of the worm wheel.
  • the engaging surface of the other side and the axial side, the first acting surface and the second acting surface of the worm 2 refer to the engaging surfaces of the teeth (tooth portions) of the worm on the axial side and the other side in the axial direction.
  • the present invention provides a worm gear mechanism capable of adjusting the axial tooth gap of the worm gear when the rotation direction of the worm is changed, which can greatly reduce the wear of the worm gear mechanism.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear Transmission (AREA)
  • Gears, Cams (AREA)

Abstract

一种能够调整蜗轮（1）和蜗杆（2）的轴向齿间隙的蜗轮蜗杆机构，所述的蜗轮蜗杆机构包括彼此啮合的蜗轮（1）和蜗杆（2），蜗杆（2）能够相对于蜗轮（1）在第一轴向极限位置和第二轴向极限位置之间轴向移动；当蜗杆（2）处于第一轴向极限位置时，蜗杆（2）绕第一转动方向转动，蜗杆（2）的齿部的第一作用面抵靠蜗轮（1）的齿部的第一作用面；当蜗杆（2）处于第二轴向极限位置时，蜗杆（2）绕第二转动方向转动，蜗杆（2）的齿部的第二作用面抵靠蜗轮（1）的齿部的第二作用面。所述的蜗轮蜗杆机构能够在蜗杆（2）的转动方向变化时调整蜗轮（1）蜗杆（2）的轴向齿间隙，其能够大幅降低蜗轮蜗杆机构的磨耗。

Description

蜗轮蜗杆机构
相关申请的引用
本发明要求2016年6月6日在中国提交的、名称为“蜗轮蜗杆机构”、申请号为201610392433.5的发明专利申请的优先权，该申请的全部内容通过引用并入本文。
技术领域
本发明涉及蜗轮蜗杆领域，具体地涉及能够调整蜗轮和蜗杆的轴向齿间隙的蜗轮蜗杆机构。
背景技术
在现有技术的蜗轮蜗杆机构中，如图1a和图1b所示，该蜗轮蜗杆机构包括彼此啮合的蜗轮10和蜗杆20，驱动齿轮30位于蜗杆20的轴向一侧并且蜗杆20与驱动齿轮30固定连接或形成为一体以构成组合件，该组合件能够在转轴40上转动。另外，该蜗轮蜗杆机构还包括安装于转轴40且分别位于驱动齿轮30的轴向一侧(图中的左侧)和蜗杆20的轴向另一侧(图中的右侧)的挡圈50、60，该挡圈50、60用作蜗杆20与驱动齿轮30在轴向A上的止挡件。挡圈50与驱动齿轮30的轴向一侧的端面抵接在一起，挡圈60与蜗杆20的轴向另一侧的端面抵接在一起，这样使得蜗杆20和驱动齿轮30在转轴40上不会相对于蜗轮10产生轴向移动。
在如图1a和图1b所示的现有技术的蜗轮蜗杆机构中，由于蜗轮10与蜗杆20啮合之后它们的齿在轴向A上具有轴向齿间隙L，因此当驱动齿轮30的转动方向转换时，蜗杆20在驱动齿轮30的驱动力的作用下通过转动快速消除该轴向齿间隙L而在蜗杆20的齿部和涡轮10的齿部之间产生碰撞冲击，从而导 致蜗轮10和蜗杆20产生非常严重的磨耗。
发明内容
基于上述现有技术中的缺陷而做出了本发明。为此，本发明采用如下的技术方案。
本发明提供了一种如下的蜗轮蜗杆机构，所述蜗轮蜗杆机构包括彼此啮合的蜗轮和蜗杆，所述蜗杆能够相对于所述蜗轮在第一轴向极限位置和第二轴向极限位置之间轴向移动，并且当所述蜗杆处于所述第一轴向极限位置时，所述蜗杆绕第一转动方向转动，所述蜗杆的齿部的第一作用面抵靠所述蜗轮的齿部的第一作用面；当所述蜗杆处于所述第二轴向极限位置时，所述蜗杆绕第二转动方向转动，所述蜗杆的齿部的第二作用面抵靠所述蜗轮的齿部的第二作用面。
优选地，所述蜗轮蜗杆机构还包括：驱动件，所述驱动件能够驱动所述蜗杆轴向移动；和/或限位结构，所述限位结构能够将所述蜗杆限定于所述第一轴向极限位置和所述第二轴向极限位置。
更优选地，所述驱动件具有不同的转动方向，通过改变所述驱动件的转动方向来驱动所述蜗杆轴向移动。
进一步，优选地，所述驱动件为驱动齿轮，所述驱动齿轮还作为驱动所述蜗杆进行转动的驱动源。
优选地，所述限位结构包括分别设置于所述蜗杆的轴向两侧的两个止挡件，所述两个止挡件中的一个止挡件的止挡面能够将所述蜗杆限定于所述第一轴向极限位置，所述两个止挡件中的另一个止挡件的止挡面能够将所述蜗杆限定于所述第二轴向极限位置。
更优选地，所述一个止挡件能够驱动所述蜗杆轴向移动。
更优选地，当所述蜗杆处于所述第一轴向极限位置的状态下，所述蜗杆 与所述另一个止挡件的止挡面之间的间隙小于或等于该状态下的所述蜗杆的齿部的第二作用面与所述蜗轮的齿部的第二作用面之间的轴向齿间隙；和/或当所述蜗杆处于所述第二轴向极限位置的状态下，所述蜗杆与所述一个止挡件的止挡面之间的间隙小于或等于该状态下的所述蜗杆的齿部的第一作用面与所述蜗轮的齿部的第一作用面之间的轴向齿间隙。
优选地，所述蜗杆在靠近所述驱动件的部分形成有蜗杆螺纹部，并且所述驱动件具有用于与所述蜗杆螺纹部啮合的驱动件螺纹部，所述驱动件通过彼此啮合的所述蜗杆螺纹部和所述驱动件螺纹部的相对转动来驱动所述蜗杆轴向移动。
优选地，所述蜗轮蜗杆机构还包括转轴，所述蜗杆以能够沿着所述轴向在所述转轴上相对于所述蜗轮移动的方式安装于所述转轴。
优选地，所述限位结构为插销结构或锁扣结构。
通过采用上述技术方案，本发明提供了一种能够在蜗杆的转动方向变化时调整蜗轮蜗杆的轴向齿间隙的蜗轮蜗杆机构，其能够大幅降低蜗轮蜗杆机构的磨耗。
附图说明
图1a是示出了现有技术的蜗轮蜗杆机构的立体示意图；图1b是示出了现有技术的蜗轮蜗杆机构的主视示意图。
图2a是示出了根据本发明的蜗轮蜗杆机构的立体示意图；图2b是示出了根据本发明的蜗轮蜗杆机构的主视示意图。
图3a是示出了当蜗杆处于第一轴向极限位置时根据本发明的蜗轮蜗杆的啮合状态示意图；图3b是示出了当蜗杆处于第二轴向极限位置时根据本发明的蜗轮蜗杆的啮合状态示意图。
附图标记说明
10蜗轮  20蜗杆  30驱动齿轮  40转轴  50、60挡圈
1蜗轮  2蜗杆  21内螺纹部  3驱动齿轮  31外螺纹部  4转轴  5、6挡圈
L轴向齿间隙  A轴向  D间隙
具体实施方式
以下参照说明书附图来说明本发明的具体实施方式。在附图中，标记A表示“轴向”、即沿着蜗杆的中心轴线的方向；另外，除非特别指明，否则“轴向一侧”指图中的左侧、“轴向另一侧”指图中的右侧。在本发明中，“轴向齿间隙L”是指蜗轮和蜗杆在啮合之后相邻的齿在上述轴向上的间隙；并且在本发明中所涉及的“间隙”或“间隔”均是指在上述轴向上的间隙或间隔。
(蜗轮蜗杆机构的概略结构)
如图2a和图2b所示，在本实施方式中，根据本发明的蜗轮蜗杆机构包括蜗轮1、蜗杆2、驱动齿轮3、转轴4和两个挡圈5、6。
如图所示，蜗轮1和蜗杆2彼此啮合在一起，用作驱动件的驱动齿轮3位于蜗杆2的轴向一侧。与现有技术不同地，蜗杆2与驱动齿轮3是单独的部件(彼此之间无连接)并且蜗杆2能够相对于蜗轮1沿着轴向A移动到第一轴向极限位置和第二轴向极限位置。驱动齿轮3设置有中心安装孔，蜗杆2设置有沿着其中心轴线延伸且贯通整个蜗杆2的中心通孔。转轴4分别穿过驱动齿轮3的中心安装孔和蜗杆2的中心通孔，使得驱动齿轮3和蜗杆2安装于转轴4。
在本实施方式中，驱动齿轮3不仅能够驱动蜗杆2绕着转轴4转动、还能够驱动蜗杆2沿着轴向A相对于蜗轮1(驱动齿轮3)移动。但是在本发明中，该实施方式仅为一种结构简单、节约成本的实现方式。为了实现蜗杆2沿轴向A移动的功能，可选地，可以通过另外的驱动结构来实现蜗杆2单纯地沿轴 向A移动而不产生转动。
另外，在本实施方式中，蜗轮蜗杆机构还包括安装于转轴4且分别位于驱动齿轮3的轴向一侧和蜗杆2的轴向另一侧的挡圈5、6，这样使得驱动齿轮3和蜗杆2在轴向A上位于挡圈5、6之间。挡圈5、6均不能沿着轴向在转轴4上移动。挡圈5安装于转轴4并始终与驱动齿轮3的轴向一侧的端面抵接在一起；挡圈6同样安装于转轴4，但是在驱动齿轮3驱动蜗杆2沿着不同方向转动的情况下挡圈6与蜗杆2具有不同的相对状态(以下详述)。
在本实施方式中，驱动齿轮3用作蜗杆2的轴向一侧的止挡件，通过驱动齿轮3的轴向另一侧的端面(止挡面)限定蜗杆2的第一轴向极限位置；挡圈6用作蜗杆2的轴向另一侧的止挡件，通过挡圈6的轴向一侧的端面(止挡面)限定蜗杆2的第二轴向极限位置。
这样，当驱动齿轮3沿不同的转动方向驱动蜗杆2时，蜗杆2能够分别移动到上述第一轴向极限位置和上述第二轴向极限位置，进而能够调整在蜗杆2处于不同转动方向时蜗轮1的齿和蜗杆2的齿之间的抵接状态。
(驱动齿轮3和蜗杆2之间的驱动结构)
为了通过驱动齿轮3驱动蜗杆2实现轴向移动以及绕着转轴4的转动，蜗杆2在轴向一侧的部分形成有内螺纹部21、即在蜗杆2的中心通孔的轴向一侧的周面上设置有内螺纹部21。相应地，驱动齿轮3的轴向另一侧的端面处设置有用于与内螺纹部21啮合的外螺纹部31，该外螺纹部31设置于从驱动齿轮3的轴向另一侧的端面突出并伸入到蜗杆2的中心通孔中的突出部。
在本实施方式中，优选地，该外螺纹部31的轴向A上的长度大于该内螺纹部21的轴向A上的长度。
这样，驱动齿轮3通过彼此啮合的内螺纹部21和外螺纹部31可以驱动蜗杆2沿着轴向A相对于蜗轮1移动、进而带动蜗杆2绕着转轴4转动，具体过程在随后的内容中详细说明。
(蜗杆2沿着轴向A相对于蜗轮1能够移动的距离)
如图3a所示，当蜗杆2处于第一轴向极限位置时，蜗杆2与驱动齿轮3抵接在一起，蜗轮1的齿在轴向另一侧的第一作用面和蜗杆2的齿在轴向一侧的第一作用面彼此抵接。此时，蜗轮1的齿在轴向一侧的第二作用面和蜗杆2的齿在轴向另一侧的第二作用面具有轴向齿间隙L，在蜗杆2的轴向另一侧的端面与挡圈6的轴向一侧的端面(止挡面)之间具有间隙D，使得间隙D等于轴向齿间隙L。
如图3b所示，当蜗杆2处于第二轴向极限位置时，蜗杆2与挡圈6抵接在一起，蜗轮1的齿的第二作用面与蜗杆2的齿的第二作用面彼此抵接。此时，蜗轮1的齿的第一作用面和蜗杆2的齿的第一作用面具有轴向齿间隙L，在驱动齿轮3的轴向另一侧的端面(止挡面)与蜗杆2的轴向一侧的端面之间具有间隙D，使得间隙D等于轴向齿间隙L。
这样，当蜗杆2的转动方向发生变化时，蜗杆2能够沿着轴向A相对于蜗轮1移动的预定距离(等于间隙D)等于轴向齿间隙L，进而缓冲由于蜗杆2的转动方向发生变化时在蜗轮1与蜗杆2之间发生的剧烈碰撞。另外，在其它实施方式中，还可以使得上述间隙D小于轴向齿间隙L。
以上具体说明了本发明的一实施方式的蜗轮蜗杆机构的结构特征，下面说明蜗轮蜗杆机构的工作过程。
(蜗轮蜗杆机构的工作过程)
如图3a所示，在驱动齿轮3始终保持沿一个方向转动的状态下，驱动齿轮3与蜗杆2抵接在一起并形成为绕着转轴4转动的整体。在该状态下，蜗轮2处于第一轴向极限位置并且蜗轮1的齿的第一作用面与蜗杆2的齿的第一作用面彼此抵接，间隙D位于蜗杆2与挡圈6之间。在此状态下，蜗轮1进行顺时针转动。
随着驱动齿轮3从沿一个方向转动变成沿另一个方向转动，驱动齿轮3的 外螺纹部31和蜗杆2的内螺纹部21之间产生相对转动，从而蜗杆2沿着轴向A相对于蜗轮1向轴向另一侧移动。在此过程中，驱动齿轮3与蜗杆2之间的间隙增大，而蜗杆2与挡圈6之间的间隙减小。最终，蜗杆2移动到与挡圈6抵接的状态，此时，蜗轮2处于第二轴向极限位置并且蜗轮1的齿的第二作用面与蜗杆2的齿的第二作用面彼此抵接。进而蜗杆2与驱动齿轮3整体绕着转轴4转动，从而带动蜗轮1转动。该最终状态如图3b所示，这时，间隙D位于驱动齿轮3和蜗杆2之间。在此状态下，蜗轮1进行逆时针转动。
这样，通过驱动齿轮3驱动蜗杆2改变转动方向之后，不会由于轴向齿间隙L的存在对蜗轮1和蜗杆2彼此啮合的齿造成剧烈冲击，从而消除了由此带来的磨耗。
当然，如果驱动齿轮3从沿另一个方向转动变成沿一个方向转动，则上述工作流程相反，在此不进行赘述了。
但是无论驱动齿轮3的转动方向如何变换，在驱动蜗杆2沿着轴向A相对于蜗轮1移动的过程中，驱动齿轮3与蜗杆2之间的间隙和蜗杆2与挡圈6之间的间隙之和始终等于图3a和图3b中所示的间隙D的尺寸。这样也保证了蜗杆2沿着轴向A相对于蜗轮1移动的距离不会大于间隙D、从而也不会大于轴向齿间距L。这样，避免了由于蜗杆2在轴向A上移动的距离过大，从而导致对蜗轮蜗杆机构正常工作造成影响。
虽然以上阐述了根据本发明的蜗轮蜗杆机构的具体实施方式，但是仍然需要说明的是：
1.虽然在上述的具体实施方式中说明了采用驱动齿轮3作为驱动件，但是本发明不限于此。驱动件不限于驱动齿轮3，而可以采用其它的部件或结构，只要该部件和结构能够驱动蜗杆2沿着轴向A相对于蜗轮1移动即可。可选地，设置单纯地驱动蜗杆2沿着轴向A相对于蜗轮1移动的驱动结构。
2.虽然在上述具体实施方式中说明了使用驱动齿轮3限定第一轴向极限位置，但是本发明不限于此。也可以采用将驱动齿轮3设置于挡圈5、6的外侧，然后利用挡圈5、6分别限定蜗杆2的第一轴向极限位置和第二轴向极限 位置。
3.另外，还可以采用插销结构或锁扣结构等作为实现上述功能的限位结构。例如，插销结构可以通过在转轴4上设置销来将蜗杆2限定于第一轴向极限位置和第二轴向极限位置。
4.虽然在上述具体实施方式中未进行详细地说明，驱动齿轮3可以由挡圈5限位于转轴4，从而使得驱动齿轮3不能沿轴向A在转轴4上移动。当然，在本发明的其它实施方式中，可以使驱动齿轮3单独地安装于转轴4而省略上述挡圈5。
5.虽然在上述具体实施方式中未进行具体说明，但是轴向齿间隙L通常为0.05mm至0.10mm，因此上述间隙D优选地设置为小于或等于0.05mm。
6.虽然在上述具体实施方式中未进行具体说明，但是应当理解，在图3b所示的状态下，通过蜗杆2压抵挡圈6而使驱动齿轮3、蜗杆2和挡圈6一起相对于转轴4转动，所以挡圈6可以相对于转轴4转动。另外，在图3a所示的状态下，通过蜗杆2压抵驱动齿轮3而使驱动齿轮3和蜗杆2一起转动，所以挡圈5可以与驱动齿轮3一起相对于转轴4转动，挡圈5也可以与转轴4固定在一起而使驱动齿轮3相对于挡圈5转动。
7.虽然在上述具体实施方式中未进行具体说明，但是优选地，驱动齿轮3在轴向A上是不可动的。
8.在上述实施方式中，说明了在驱动齿轮3上形成外螺纹部31，在蜗杆2上形成内螺纹部21。然而，本发明不限于此，可以在蜗杆2的轴向一侧的端部形成外螺纹部，并在驱动齿轮3上对应地形成内螺纹部。
9.虽然在上述实施方式中没有具体说明，但是应当理解，蜗轮1的齿的第一作用面和第二作用面是指蜗轮的多个齿(齿部)中的每一个齿的在轴向另一侧和轴向一侧的啮合面，蜗杆2的第一作用面和第二作用面是指蜗杆的齿(齿部)的在轴向一侧和轴向另一侧的啮合面。
通过采用上述技术方案，本发明提供了一种能够在蜗杆的转动方向变化时调整蜗轮蜗杆的轴向齿间隙的蜗轮蜗杆机构，其能够大幅降低蜗轮蜗杆机构的磨耗。
本发明的保护范围不限于上述具体实施方式的具体实施例，而是只要满足本发明的技术特征的组合就落入了本发明的保护范围之内。

Claims (10)

  1. 一种蜗轮蜗杆机构，所述蜗轮蜗杆机构包括彼此啮合的蜗轮和蜗杆，其特征在于，
    所述蜗杆能够相对于所述蜗轮在第一轴向极限位置和第二轴向极限位置之间轴向移动，并且
    当所述蜗杆处于所述第一轴向极限位置时，所述蜗杆绕第一转动方向转动，所述蜗杆的齿部的第一作用面抵靠所述蜗轮的齿部的第一作用面；当所述蜗杆处于所述第二轴向极限位置时，所述蜗杆绕第二转动方向转动，所述蜗杆的齿部的第二作用面抵靠所述蜗轮的齿部的第二作用面。
  2. 根据权利要求1所述的蜗轮蜗杆机构，其特征在于，
    所述蜗轮蜗杆机构还包括：
    驱动件，所述驱动件能够驱动所述蜗杆轴向移动；和/或
    限位结构，所述限位结构能够将所述蜗杆限定于所述第一轴向极限位置和所述第二轴向极限位置。
  3. 根据权利要求2所述的蜗轮蜗杆机构，其特征在于，所述驱动件具有不同的转动方向，通过改变所述驱动件的转动方向来驱动所述蜗杆轴向移动。
  4. 根据权利要求3所述的蜗轮蜗杆机构，其特征在于，所述驱动件为驱动齿轮，所述驱动齿轮还作为驱动所述蜗杆进行转动的驱动源。
  5. 根据权利要求2至4中任一项所述的蜗轮蜗杆机构，其特征在于，所述限位结构包括分别设置于所述蜗杆的轴向两侧的两个止挡件，所述两个止挡件中的一个止挡件的止挡面能够将所述蜗杆限定于所述第一轴向极限位置，所述两个止挡件中的另一个止挡件的止挡面能够将所述蜗杆限定于所述第二轴向极限位置。
  6. 根据权利要求5所述的蜗轮蜗杆机构，其特征在于，所述一个止挡件能够驱动所述蜗杆轴向移动。
  7. 根据权利要求5所述的蜗轮蜗杆机构，其特征在于，
    当所述蜗杆处于所述第一轴向极限位置的状态下，所述蜗杆与所述另一个止挡件的止挡面之间的间隙小于或等于该状态下的所述蜗杆的齿部的第二作用面与所述蜗轮的齿部的第二作用面之间的轴向齿间隙；和/或
    当所述蜗杆处于所述第二轴向极限位置的状态下，所述蜗杆与所述一个止挡件的止挡面之间的间隙小于或等于该状态下的所述蜗杆的齿部的第一作用面与所述蜗轮的齿部的第一作用面之间的轴向齿间隙。
  8. 根据权利要求2至4中任一项所述的蜗轮蜗杆机构，其特征在于，所述蜗杆在靠近所述驱动件的部分形成有蜗杆螺纹部，并且所述驱动件具有用于与所述蜗杆螺纹部啮合的驱动件螺纹部，所述驱动件通过彼此啮合的所述蜗杆螺纹部和所述驱动件螺纹部的相对转动来驱动所述蜗杆轴向移动。
  9. 根据权利要求2至4中任一项所述的蜗轮蜗杆机构，其特征在于，所述蜗轮蜗杆机构还包括转轴，所述蜗杆以能够沿着所述轴向在所述转轴上相对于所述蜗轮移动的方式安装于所述转轴。
  10. 根据权利要求2至4中任一项所述的蜗轮蜗杆机构，其特征在于，所述限位结构为插销结构或锁扣结构。
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