WO2011069330A1 - 轴承式超越离合器结构 - Google Patents

轴承式超越离合器结构 Download PDF

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Publication number
WO2011069330A1
WO2011069330A1 PCT/CN2010/001970 CN2010001970W WO2011069330A1 WO 2011069330 A1 WO2011069330 A1 WO 2011069330A1 CN 2010001970 W CN2010001970 W CN 2010001970W WO 2011069330 A1 WO2011069330 A1 WO 2011069330A1
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WO
WIPO (PCT)
Prior art keywords
roller
star wheel
outer ring
concave curved
overrunning clutch
Prior art date
Application number
PCT/CN2010/001970
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English (en)
French (fr)
Inventor
陈菊花
Original Assignee
Chen Juhua
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Publication date
Application filed by Chen Juhua filed Critical Chen Juhua
Priority to US13/381,667 priority Critical patent/US20120132496A1/en
Publication of WO2011069330A1 publication Critical patent/WO2011069330A1/zh

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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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/064—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls
    • F16D41/066—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls all members having the same size and only one of the two surfaces being cylindrical

Definitions

  • the invention discloses a bearing type overrunning clutch structure, which belongs to the technical field of clutch manufacturing according to the International Patent Classification Table (IPC), and particularly relates to a novel structure of a loader two-shaft assembly overrunning clutch.
  • IPC International Patent Classification Table
  • Overrunning clutch also known as a one-way clutch or one-way bearing, is a device that can only transfer power from one steering.
  • the speed of the active raceway is the same as the speed of the driven raceway, when the speed of the active raceway is less than the speed of the driven raceway, the driven raceway can rotate freely.
  • the current overrunning clutches are mainly of the roller type overrunning clutch and the wedge type overrunning clutch.
  • the overrunning clutch is an extremely important component in the loader gearbox assembly. At present, most of the loader gearbox assemblies use conventional roller type overrunning clutches.
  • the general structure of the roller type overrunning clutch is mainly composed of inner ring cams, rollers, cylindrical springs, spacer rings and gland parts. When the clutch is combined, due to the structural limitation and synchronization, the number of effective working rollers is small. The working plane of the inner ring cam of the clutch is in line contact with the roller, and the surface compressive stress is too large to form an arc pit, and the friction angle is rapidly increased. Large, causing the clutch to slip and fail.
  • Chinese patent document CN 2708031 discloses an overrunning clutch including an outer ring, a star wheel, a roller and an elastic device.
  • the elastic device is installed in the hole on the tooth side of the star wheel, and pushes the roller to slide on the star wheel, and further includes a a slider that slides integrally with the roller on the star wheel and is engaged with the inner wall of the outer ring by the elastic device; further, the Chinese patent document CN 101629606 provides a multi-roller overrunning clutch having at least six rollers.
  • the spring piece has an elastic bayonet at one end, and the other end has a circular arc end portion adapted to the outer circular surface of the roller, and the elastic snap ring of the spring piece is buckled On the beam of the cage, the arc The end of the shape cooperates with the roller and pushes the roller.
  • the two roller overrunning clutches are structurally constrained. The low load carrying capacity and the unsynchronization during operation are the most deadly problems.
  • Double cage overrunning clutch comprising an inner ring with an outer raceway and an outer ring with an inner raceway, a plurality of shaped blocks between the inner and outer raceways; and an inner cage and an outer cage
  • the annular double retainer is formed, and the same number of retaining holes are evenly distributed on the inner and outer retaining frames, and the shaped retaining blocks are relatively held by the retaining holes of the circular double retainer in the annular inner and outer rolling a plurality of perforated spring strips are disposed between the inner and outer cages of the double retainer, and a plurality of shaped clips are inserted into the through holes of the spring strip; and the utility model is characterized in that: the outer retainer is provided with a plurality of Fixed reeds; a plurality of friction reeds on the inner cage.
  • the overrunning clutch ensures the synchronization during operation, since the radius of curvature of the wedge is small and the gap between the cage and the wedge is large, the wedge is liable to be tilted during loading, so that the wedge and the inner and outer raceways are There is a point contact between them, so the torque tolerated is small.
  • the present invention provides a bearing type overrunning clutch structure which can improve the load carrying capacity and prolong the service life.
  • a bearing type overrunning clutch structure includes an outer ring, an inner star wheel and a plurality of rollers disposed between the outer ring and the inner star wheel, wherein:
  • the inner star wheel has a plurality of concave curved grooves in the circumferential direction, and each concave curved groove corresponds to one roller, and the outer race of the roller is the inner cylindrical inner surface of the outer ring which is in contact with the roller, and the inner roller
  • the track is a concave curved groove on the outer cylindrical surface of the inner star wheel;
  • the inner star wheel rotates in the same direction as the outer ring, when the speed of the inner star wheel is less than or equal to the outer ring At speed nl, the roller is wedged between the inner star and the outer ring, and the clutch is in a combined state; when the speed n2 of the inner star is greater than the speed nl of the outer ring, the clutch is disengaged.
  • the outer ring is a gear outer ring
  • the outer ring is provided with an annular groove in a circumferential direction
  • the inner star wheel and the plurality of matched rollers are disposed in the annular groove to form a clutch structure, and the rollers are assembled
  • the outer raceway of the roller is the outer peripheral surface of the annular groove of the outer ring
  • the inner raceway is a concave curved groove on the inner star wheel.
  • the concave curved groove is evenly distributed on the outer cylindrical surface of the inner star wheel, and the depth L of the concave curved groove is: ⁇ L ⁇ , where d is the roller diameter, (if the depth is too shallow, the clutch is difficult Disengaged, the depth is too deep, the concave curved groove is difficult to manufacture).
  • the bus bar of the concave curved surface constituting the concave curved groove is parallel to the inner star axis.
  • the concave curved surface in the concave curved surface groove is a curved surface formed by a logarithmic spiral or an arc. Further, the pole of the logarithmic spiral forming the concave curved surface or the center of the arc and the eccentricity of the center of the roller e>0.
  • roller is kept tangent to the outer ring or the outer raceway surface of the gear outer ring.
  • the roller when the speed n2 of the inner star wheel is less than or equal to the speed nl of the outer ring, the roller is wedged between the inner star wheel and the outer ring, and the clutch is in a combined state; when the inner star wheel speed n2 is larger than the outer ring At speed nl, the clutch is disengaged.
  • the invention is characterized in that: the bearing type overrunning clutch increases the number of rollers in the same space, so that the gap s between adjacent two rollers is reduced to 0 ⁇ 0. 2mm, and the original inner star plane is Type changed to concave Curved type.
  • the bearing type overrunning clutch of the present invention removes the spring pin mechanism or the three-foot spring and the isolating ring in the existing overrunning clutch, thereby avoiding the spring due to the small number of effective working rollers. And the failure of the top pin, the excessive wear or deformation of the roller and the large gap between the spacer ring and the roller, the roller is inclined when the load is loaded, and the roller is kept in contact with the star wheel and the outer ring to cause the bearing capacity. The problem of falling.
  • the invention increases the number of rollers in the same space to reduce the roller gap, and also changes the original inner star wheel plane type to a concave curved surface type, which increases the comprehensive curvature of the contact point between the roller and the inner star wheel outer surface, thereby greatly Increased contact strength and increased torque capacity.
  • the invention has reasonable structural design, simple manufacturing process, strong working reliability, good synchronism, can withstand large torque and impact force, and can be loaded at high speed and heavy load. In case of long hours of work.
  • the bearing type overrunning clutch structure of the invention is mainly applied to a loader, and can also be applied to an airplane, a tank, a military truck, a heavy truck, an off-road vehicle, a ship, a forklift, a car, a motorcycle, a lathe, a printing machine, a textile machine, a nut.
  • Figure 1 is a partial cross-sectional view of the present invention
  • a bearing type overrunning clutch is also called a bearing type loader two-shaft assembly overrunning clutch, including outer ring 1, inner star wheel 2, and roller 3, in the outer ring.
  • a bearing type overrunning clutch is also called a bearing type loader two-shaft assembly overrunning clutch, including outer ring 1, inner star wheel 2, and roller 3, in the outer ring.
  • rollers 3 between the inner star wheel 2 and the inner star wheel 2
  • 24 concave curved grooves are arranged on the outer cylindrical surface of the inner star wheel 2, and a concave curved groove corresponds to one roller 3.
  • the concave curved surface in the concave curved groove is composed of a logarithmic spiral, because the angle between the tangent at any point on the logarithmic spiral and the polar radius P of the point (ie, the spiral angle) is The constant m, the roller from the momentary engagement to the full transmission of the torque, the angle of engagement with the inner race" remains unchanged, so the forces acting on the individual rollers are equal.
  • the inner star wheel 2 when the inner star 2 is counterclockwise When the rotation speed and the speed n2 are less than or equal to the speed n1 of the outer ring 1, the roller is engaged at this time, the inner star wheel 2 drives the outer ring 1 to rotate by the roller 3, and the clutch is in the combined state P1, as indicated by the solid line in FIG. 2;
  • the clutch is in the disengaged state P2, as indicated by the broken line in FIG.
  • the outer ring 1 is a gear outer ring, which is composed of a ring body 11 and a plurality of teeth 12 on the outer peripheral side thereof, and the ring body is provided with an annular groove in the circumferential direction.
  • the slot penetrates through an end surface of the outer ring of the gear, and the inner star wheel 2 and the plurality of matched rollers 3 are disposed in the annular groove to form a clutch structure, and the rollers are assembled on the outer cylindrical surface of the inner star wheel.
  • the outer race of the roller is the outer circumferential surface of the annular groove with the outer ring, and the inner race is the concave curved groove on the inner star wheel.
  • the above structure is assembled on the rotating shaft 4, one end of the rotating shaft ( The left end) radially extends to form a rotating shaft end cover 40, which is fastened to the inner star wheel 2 by bolts 5 and nuts, and the gear outer ring and the inner star wheel are relatively rotatable, His structure is the same as the technical solution of the present invention.
  • the inner cylindrical surface of the outer ring has a diameter of 210 mm, the roller diameter is 24.23 mm, the roller length is 32 mm, and the outer diameter of the inner star wheel and the roller contact point is 162 mm, the roller and the inner and outer raceway surfaces.
  • the engagement angle is 3.75°, the gap between the roller and the roller is 0.02 mm, the radius of curvature of the contact point between the roller and the star wheel surface is 15 mm, and the radius of curvature of the contact point between the roller and the outer raceway is 105.
  • the number of wedges in the wedge type overrunning clutch is 44, the width of the wedge is 20.5mm, and the radius of curvature of the contact point between the wedge and the inner and outer raceways is 7.85, the outer surface diameter of the inner ring is 184.18, the meshing angle ⁇ of the wedge and the outer surface of the inner race is 3.4°; the meshing angle ⁇ of the wedge and the inner surface of the outer race is 2.58°; the wedge and the outer race are known by Hertz theory.
  • Z the number of rollers or wedges
  • R raceway radius
  • the gap between the roller and the roller in the two-axle assembly of the bearing loader is small, only 0. 02mm, when the clutch is in the combined state, one roller is engaged and loaded, between the roller and the roller Through linkage, all the rollers are synchronously loaded, thus ensuring full synchronism during operation.

Description

轴承式超越离合器结构 技术领域
发明公开一种轴承式超越离合器结构， 按国际专利分类表 (IPC)划分属于 离合器制造技术领域， 尤其是涉及一种装载机二轴总成超越离合器的新型结构。 背景技术
超越离合器又称单向离合器或单向轴承，是一种只能从一个转向传递功率的 装置。 当主动滚道的速度与从动滚道的速度相同时进行传递， 而当主动滚道的 速度小于从动滚道的速度时， 从动滚道能自由转动。
目前的超越离合器主要有滚柱式超越离合器和楔块式超越离合器两种，超越 离合器是装载机变速箱总成中一个极其重要的部件。 目前， 装载机变速箱总成 大部分都是采用传统滚柱式超越离合器， 滚柱式超越离合器的一般结构主要是 由内环凸轮、 滚柱、 圆柱弹簧、 隔离环和压盖等零件组成， 当离合器结合时， 由于结构限制及同步性原因， 有效工作的滚柱数量较少， 离合器内环凸轮的工 作平面与滚柱为线接触， 表面压应力过大而形成弧坑， 摩擦角迅速增大， 造成 离合器打滑而失效。 中国专利文献 CN 2708031 公开了一种超越离合器，包括外 环、 星轮、 滚柱及弹性装置,弹性装置安设于星轮齿侧的孔中，并推动滚柱滑行 于星轮，还包括一滑块，与滚柱一体滑行于星轮，并在弹性装置推动下与外环内 壁相接合； 另外中国专利文献 CN 101629606 提供了一种多滚柱式超越离合器， 它具有至少六个滚柱、 内星轮式外圈、 保持架和与滚柱个数相同的弹簧片， 保 持架紧配在内星轮式外圈内， 滚柱放置在端环和横梁形成的各窗口中、 且处于 内星轮式外圈的各内凹弧形楔面部位；弹簧片一端具有弹性卡口、 另一端为与滚 柱的外圆面相适配的圆弧形端部，弹簧片的弹性卡口扣在保持架的横梁上，圆弧 形端部与滚柱配合并推紧滚柱， 上面两种滚柱式超越离合器受结构限制， 承载 能力低和工作时的不同步性是其最为致命的问题。
而楔块式超越离合器在技术上也存在不足之处， 如本申请人曾于 2003 年 12月 13号申请的名称为"双保持架超越离合器 "的申请，申请号为 03102580. 3, 涉及一种双保持架超越离合器,包括具有外滚道的内环和具有内滚道的外环，在 内、 外滚道之间设有多个异型卡块;设有由内保持架和外保持架所构成的圆环形 双保持架，且在内、 外保持架上均布有相同数量的保持孔,所述异型卡块被圆环 形双保持架的保持孔相对保持于所述环形内外滚道内；该双保持架的内、 外保持 架之间均布有多个穿孔的弹簧带，多个异型卡块插设于该弹簧带的穿孔中；其特 征是：在外保持架上设有多个固定簧片；在内保持架上设有多个摩擦簧片。 上述 超越离合器虽然保证了工作时的同步性， 但是由于楔块的曲率半径小， 且保持 架与楔块之间的间隙较大， 受载时楔块易发生倾斜， 使楔块与内外滚道之间是 点接触， 故承受的扭矩小。
发明内容
针对现有离合器技术的不足， 本发明提供了一种既能提高受载能力， 又能 延长使用寿命的轴承式超越离合器结构。
为达到上述目的， 本发明是通过以下技术方案实现的：
一种轴承式超越离合器结构， 其包括外圈、 内星轮及设置于外圈与内星轮 之间的多个滚柱， 其中：
内星轮， 其外侧圆柱面沿周向设有多个凹形曲面槽， 每个凹形曲面槽分别 对应一个滚柱， 滚柱的外滚道为与滚柱接触的外圈内侧圆柱面， 内滚道为内星 轮外侧圆柱面上的凹形曲面槽；
所述的内星轮与外圈同向相对转动， 当内星轮的速度 n2小于或等于外圈的 速度 nl时， 滚柱在内星轮与外圈之间被楔紧， 离合器处于结合状态； 当内星轮 的速度 n2大于外圈的速度 nl时， 离合器处于脱开状态。
进一步， 所述的外圈为齿轮外圈， 该外圈沿周向设有环形凹槽， 内星轮及 与相配合的多个滚柱设置于上述环形凹槽内形成离合器构造， 各滚柱装配于内 星轮外侧圆柱面的对应凹形曲面槽内， 滚柱的外滚道为与外圈环形凹槽的外侧 周面， 内滚道为内星轮上的凹形曲面槽。
进一步， 所述的轴承式超越离合器中相邻滚柱之间的间隙 s=a-2r=0〜 0.2mm, 其中 a为相邻滚柱的中心距， r为滚柱半径；
当离合器处于结合状态时， 一个滚柱啮合受载， 滚柱与滚柱之间通过联动， 使全部滚柱同步受载， 从而保证了工作时的全同步性。
进一步， 所述的凹形曲面槽均匀等分分布于内星轮外侧圆柱面上， 凹形曲 面槽的深度 L为： ^<L< ,其中 d为滚柱直径，（如果深度太浅离合器难以脱开， 深度太深凹形曲面槽难以制造）。
进一步， 所述的构成凹形曲面槽的凹形曲面的母线与内星轮轴线平行。 进一步， 所述凹形曲面槽内的凹形曲面是由对数螺旋线或圆弧构成的曲面。 进一步， 所述构成凹形曲面的对数螺旋线的极点或圆弧的圆心与滚柱中心 的偏心距 e〉0。
进一步， 所述的滚柱与外圈或的齿轮外圈外滚道面保持相切。
本发明当内星轮的速度 n2小于或等于外圈的速度 nl时， 滚柱在内星轮与 外圈之间被楔紧， 离合器处于结合状态； 当内星轮的速度 n2大于外圈的速度 nl 时， 离合器处于脱开状态。
本发明的特点在于： 轴承式超越离合器在相同的空间内增加了滚柱的数量， 使相邻两个滚柱之间的间隙 s减小到 0〜0. 2mm, 并把原内星轮平面型改为凹形 曲面型。 此设计的优点如下：
1、 提高了离合器的承载能力： 本发明轴承式超越离合器去除了现有超越离 合器中的弹簧顶销机构或三尺弹簧和隔离环， 从而避免了因有效工作的滚柱数 量较少而导致弹簧及顶销的失效、 滚柱的过度磨损或变形和因隔离环与滚柱之 间的间隙较大， 受载时滚柱发生倾斜， 使滚柱与星轮和外圈保持点接触导致承 载能力下降的问题。 本发明在相同空间内增加滚柱数量减小滚柱间隙， 还把原 内星轮平面型改为凹形曲面型， 增大了滚柱与内星轮外表面接触点的综合曲率， 从而大大提高了接触强度、 增大了扭矩容量。
2、 实现了离合器的全同步性： 相邻滚柱之间的间隙 s=0〜0. 2mm。 当离合器 处于结合状态时， 一个滚柱啮合受载， 滚柱与滚柱之间通过联动， 使全部滚柱 同步受载， 从而保证了工作时的全同步性。
因此， 在相同空间上与已有的超越离合器相比， 本发明结构设计合理， 制 造工艺简单， 工作可靠性强， 同步性好， 能承受较大的扭矩和冲击力， 可在高 速重载的情况下长时间工作。
本发明轴承式超越离合器结构， 主要应用于装载机， 同时还可以应用于飞 机、 坦克、 军用卡车、 重型卡车、 越野汽车、 轮船、 叉车、 汽车、 摩托车、 车 床、 印刷机械、 纺织机械、 螺母成型机、 弹簧机、 生产线的间歇传动机械、 矿 山机械、 扳手等。
附图说明
图 1是本发明局部剖面示意图；
图 2是轴承式装载机二轴总成超越离合器运动状态分析局部剖面示意图； 图 3是轴承式装载机二轴总成超越离合器角度分析局部剖面示意图； 图 4是本发明离合器另一实施例装配侧剖图；
图中各部件标识：
1、 外圈，
2、 内星轮， 20.凹形曲面槽， 3、 滚柱，
4、 转轴， 40、 转轴端盖，
5、 螺栓。
具体实施方式
下面结合附图对本发明作进一步说明：
实施例： 请参阅图 1， 一种轴承式超越离合器在装载机中的应用又称为轴 承式装载机二轴总成超越离合器， 包括外圈 1、 内星轮 2、 滚柱 3， 在外圈 1与 内星轮 2之间设有 24个滚柱 3，内星轮 2的外侧圆柱面上设有 24个凹形曲面槽， 一个凹形曲面槽对应一个滚柱 3。 如图 3，凹形曲面槽中的凹形曲面是由对数螺 旋线构成的， 由于对数螺旋线上任一点处的切线与该点极半径 P的夹角 ^ (即螺 线距角）为常数 m， 滚柱从瞬时啮合到充分传递扭矩， 与内滚道的啮合角 "保持 不变， 所以作用于各个滚柱上的力均等。 如图 2中所示，当内星轮 2逆时针转动 且其速度 n2小于或等于外圈 1的速度 nl时， 此时滚柱啮合， 内星轮 2通过滚 柱 3带动外圈 1转动， 离合器处于结合状态 Pl， 如图 2中实线表示； 当内星轮 2的速度 n2大于外圈 1的速度 nl时， 离合器处于脱开状态 P2， 如图 2中虚线 表示。
图 4公开一种轴承式超越离合器结构， 所述的外圈 1为齿轮外圈， 其是由 圈体 11及其外周侧沿均设有若干轮齿 12组成， 圈体沿周向设有环形凹槽， 其 槽口贯穿于齿轮外圈的一端面， 内星轮 2及与相配合的多个滚柱 3设置于上述 环形凹槽内形成离合器构造， 各滚柱装配于内星轮外侧圆柱面的对应凹形曲面 槽内， 滚柱的外滚道为与外圈环形凹槽的外侧周面， 内滚道为内星轮上的凹形 曲面槽， 上述结构装配于转轴 4上， 转轴一端 (左端)径向延伸形成转轴端盖 40， 其通过螺栓 5及螺母与内星轮 2紧固， 上述齿轮外圈与内星轮可相对转动， 其 他结构与本发明技术方案相同。
本发明实施例中， 外圈内侧圆柱面的直径为 210mm，滚柱直径为 24.23mm, 滚柱长度为 32mm， 内星轮与滚柱接触点的外径为 162mm， 滚柱与内外滚道表面 的啮合角为 3.75° ， 滚柱与滚柱之间的间隙为 0.02mm，滚柱与星轮曲面接触点 的曲率半径为 15mm，滚柱与外滚道接触点的曲率半径为 105。 根据赫兹理论可知 滚柱与外圈内表面接触点的综合曲率 Q=^ =^^ =13.7,滚柱与内星轮
RL— r2 105-12.115 外表面接触点的综合曲率 Q=^^=^ ^=63， （式中 ^为滚柱半径， 为
RL -r2 15-12.115 滚柱与内外滚道接触点的曲率半径。）
在相同的空间内（即外圈内侧圆柱面的直径为 210mm)，楔块式超越离合器 中楔块数量为 44个， 楔块宽度为 20.5mm，楔块与内外滚道接触点的曲率半径为 7.85，内圈外表面直径为 184.18,楔块与内滚道外表面的啮合角 α为 3.4° ； 楔 块与外滚道内表面的啮合角 β为 2.58° ； 由赫兹理论可知楔块与外滚道内表面 接触点的综合曲率 Q=^^=1Q5x7'85=8.48，楔块与内滚道外表面接触点的综合
RL -r2 105-7.85 曲率 kg · mm'2 (s通常取值为 310-330
Figure imgf000008_0001
kg · mm ) 根据公式： M=2Z · Q · R · b · tg β ·
Figure imgf000008_0002
式中： M: 整个离合器所传递的扭矩；
Z: 滚柱或楔块的数量；
Q: 单个滚柱或楔块与滚道表面接触点的综合曲率;
R:滚道半径；
b: 单个滚柱或楔块的宽度（以 mm为单位）； β : 滚柱或楔块与滚道表面的啮合角。 对于楔块式超越离合器有- 在外滚道上为：
330
Μ=2Ζ · Q · R · b · tg ^ s max ] =2x44x8. 48x105x20. 5x0. 045x
86.12 S6A
=1061832Kg · mm « 10406 (N · m) 在内滚道上为:
330
M=2Z · Q · R · b · tg β · ^i =2x44x7. 23x92. 09x20. 5x0. 0594x
86.12 86Λ
=1048082 Kg · mm « 10271 (N · m) 对于轴承式装载机二轴总成超越离合器有：
在外滚道上为：
M=2Z · Q · R · b · tg ^ · [S
86a.x =2x
1f 24x13. 7x105x32x0. 065x 33°2
86.
=2109774 g · mm « 20676 (N · m) 在内滚道上为
3302
M=2Z · Q · R · b · tg P [S max ] =2x24x63x81x32x0. 065x
86.12 86.12
=7484309 Kg · mm « 73346 ( N · m ) 通过以上计算对比可得到： 轴承式装载机二轴总成超越离合器所传递的扭 矩远大于楔块式超越离合器所传递的扭矩。
该轴承式装载机二轴总成超越离合器中滚柱与滚柱之间的间隙很小， 只有 0. 02mm, 当离合器处于结合状态时， 一个滚柱啮合受载， 滚柱与滚柱之间通过 联动， 使全部滚柱同步受载， 从而保证了工作时的全同步性。
以上所记载， 仅为利用本创作技术内容的实施例， 任何熟悉本项技艺者运 用本创作所做的修饰、 变化， 皆属本创作主张的专利范围， 而不限于实施例所

Claims

1、 一种轴承式超越离合器结构， 其特征在于： 包括外圈、 内星轮及设置于 外圈与内星轮之间的多个滚柱， 其中： 内星轮， 其外侧圆柱面沿周向设有多个凹形曲面槽， 每个凹形曲面槽分别 对应一个滚柱， 滚柱的外滚道为与滚柱接触的外圈内侧圆柱面， 内滚道为内星 轮外侧圆柱面上的凹形曲面槽； 所述的内星轮与外圈同向相对转动， 当内星轮的速度 n2小于或等于外圈的 速度 nl时， 滚柱在内星轮与外圈之间被楔紧， 离合器处于结合状态； 当内星轮 的速度 n2大于外圈的速度 nl时， 离合器处于脱开状态。
2、 根据权利要求 1所述的轴承式超越离合器结构， 其特征在于： 所述的外 圈为齿轮外圈， 其沿周向设有环形凹槽， 内星轮及与相配合的多个滚柱设置于 上述环形凹槽内形成离合器构造， 各滚柱装配于内星轮外侧圆柱面的对应凹形 曲面槽内， 滚柱的外滚道为与外圈环形凹槽的外侧周面， 内滚道为内星轮上的 凹形曲面槽。
3、 根据权利要求 1或 2所述的轴承式超越离合器结构， 其特征在于： 所述 的轴承式超越离合器中相邻滚柱之间的间隙 s=a-2r=0〜0.2mm，
其中 a为相邻滚柱的中心距， r为滚柱半径； 当离合器处于结合状态时， 一个滚柱啮合受载， 滚柱与滚柱之间通过联动， 使全部滚柱同步受载， 从而保证了工作时的全同步性。
4、 根据权利要求 1或 2所述的轴承式超越离合器结构， 其特征在于： 所述 的凹形曲面槽均匀等分分布于内星轮外侧圆柱面上， 凹形曲面槽的深度
L: A〈L〈 ，其中 为滚柱直径。
10 2
5、 根据权利要求 1或 2所述的轴承式超越离合器结构， 其特征在于： 所述 构成凹形曲面槽的凹形曲面的母线与内星轮轴线平行。
6、 根据权利要求 4所述的轴承式超越离合器结构， 其特征在于： 所述构成 凹形曲面槽的凹形曲面的母线与内星轮轴线平行。
7、 根据权利要求 1或 2所述的轴承式超越离合器结构， 其特征在于： 所述 凹形曲面槽内的凹形曲面是由对数螺旋线或圆弧构成的曲面。
8、 根据权利要求 7所述的轴承式超越离合器结构， 其特征在于： 所述构成 凹形曲面的对数螺旋线的极点或圆弧的圆心与滚柱中心的偏心距 e〉0。
9、 根据权利要求 1或 2所述的轴承式超越离合器结构， 其特征在于： 所述 的滚柱与外圈或的齿轮外圈外滚道面保持相切。
10、 根据权利要求 2所述的轴承式超越离合器结构， 其特征在于： 所述的 齿轮外圈是由圈体及其外周侧沿均设有若干轮齿组成， 圈体沿周向设有环形凹 槽， 其槽口贯穿于齿轮外圈的一端面。
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