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WO2008022489A1 - Appareil de transmission d'énergie cinétique - Google Patents

Appareil de transmission d'énergie cinétique Download PDF

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Publication number
WO2008022489A1
WO2008022489A1 PCT/CN2006/002106 CN2006002106W WO2008022489A1 WO 2008022489 A1 WO2008022489 A1 WO 2008022489A1 CN 2006002106 W CN2006002106 W CN 2006002106W WO 2008022489 A1 WO2008022489 A1 WO 2008022489A1
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WO
WIPO (PCT)
Prior art keywords
shaft
gear
kinetic energy
energy generating
transmission
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/CN2006/002106
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English (en)
French (fr)
Inventor
Chuy-Nan Chio
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Individual
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Individual
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Publication date
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Priority to PCT/CN2006/002106 priority Critical patent/WO2008022489A1/zh
Publication of WO2008022489A1 publication Critical patent/WO2008022489A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16H—GEARING
    • F16H21/00—Gearings comprising primarily only links or levers, with or without slides
    • F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
    • F16H21/16—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for interconverting rotary motion and reciprocating motion
    • F16H21/18—Crank gearings; Eccentric gearings
    • F16H21/22—Crank gearings; Eccentric gearings with one connecting-rod and one guided slide to each crank or eccentric
    • F16H21/30—Crank gearings; Eccentric gearings with one connecting-rod and one guided slide to each crank or eccentric with members having rolling contact
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases
    • F02F7/0043—Arrangements of mechanical drive elements

Definitions

  • the present invention relates to a kinetic energy generating device, and more particularly to a kinetic energy generating device which reduces lateral component load loss, increases output power, has low rotational speed, high torque, and reduces vibration in a limited space.
  • the conventional engine operating mode is shown in Fig. 22.
  • a driving member x2 is pushed by the cylinder piston x1 to rotate the crank shaft x3 to generate a kinetic energy output.
  • the transmission member x2 since the moving direction of the transmission member x2 has a considerable lateral pressure angle, a considerable lateral component force is generated, resulting in loss of the overall kinetic energy; in addition, when the conventional engine is at the top dead center, The inertial forces of the force point x4 and the crankshaft x3 cancel each other out, which not only causes loss of kinetic energy, but also causes oscillation, resulting in engine damage and shortened life.
  • the traditional engine must pass four steps of intake, compression, explosion and exhaust every time.
  • the crank has been rotated twice around the output shaft, that is, each explosion stroke must push the engine output for two revolutions, so the output torque is better.
  • the engine must increase the speed, or increase the cylinder capacity, to provide greater torque for the engine.
  • the main advantage of the present invention is to provide a kinetic energy generating device which has a dense explosion stroke and can obtain a higher output power at a lower rotational speed to form a structure having a low rotational speed and a high torque.
  • Another object of the present invention is to provide a kinetic energy generating device which has a small change in the inertia angle of the applied force, reduces oscillation, component loss, and improves kinetic energy output.
  • Still another object of the present invention is to provide a kinetic energy generating device which is configured to have a maximum number of cylinders in a limited space by means of an inner casing, so that the overall output kinetic energy is greatly increased.
  • a further object of the present invention is to provide a kinetic energy generating device that is suitable for use in a variety of vertical and horizontal engines, even air compressor structures or other power machines.
  • Another object of the present invention is to provide a kinetic energy generating device, wherein the cylinder configuration can be operated separately for a multi-cylinder, multi-angle, and multi-track lines, so that the total output force thereof is greatly increased.
  • the kinetic energy generating device can achieve the foregoing objective, and includes a casing.
  • the casing is provided with a fixed gear on one side thereof.
  • the fixed gear has a tooth profile facing inward, and a movable gear is disposed on the inner side of the fixed gear.
  • the fixed gear and the movable gear can be meshed with each other, and the gear ratio of the fixed gear to the movable gear is 3:2; another transmission member is pivoted inside the casing as an engine kinetic energy output, and the transmission member faces the movable gear
  • the shaft center penetrates and pivots a transmission shaft, so that the transmission shaft and the movable gear are all included in the volume range of the fixed gear, and a flywheel 5 is fixedly connected to the outer side of the movable gear to rotate the flywheel synchronously with the movable gear.
  • One end of the flywheel is provided with a force applying shaft, and the shaft of the force applying shaft is provided with a connecting rod, one end of the connecting rod is arranged on the flywheel applying shaft, and the other end is arranged on the piston of the cylinder, so that the piston is on the cylinder wall
  • the reciprocating motion causes the piston to rotate the flywheel and the movable gear via the connecting rod to perform kinetic energy transmission.
  • Figure 1 is a perspective view showing the structure of the present invention
  • Figure 2 is a front elevational view of the structure of the present invention.
  • Figure 3 is a side view of the two-cylinder arrangement structure of the present invention.
  • Figure 4 is a front elevational view showing the structure of the piston and the connecting rod of the present invention.
  • Figure 5 is a two-cylinder active trajectory diagram of the present invention.
  • Figure 14 is a motion trajectory analysis diagram of the present invention
  • Figure 15 is a diagram showing the height adjustment trajectory analysis of the urging shaft of the present invention
  • Figure 16 is a diagram showing the trajectory analysis of the height adjustment axis of the urging shaft of the present invention.
  • Figure 17 is a front elevational view showing a structural change of the present invention.
  • Figure 18 is a side view showing a structural change of the present invention.
  • Figure 19 is a side view showing another structural modification of the present invention.
  • Figure 20 is a front elevational view showing another structural modification of the present invention.
  • Figure 21 is a diagram showing a variation of the transmission structure of the present invention.
  • Figure 22 is a schematic view showing the operation of a conventional crankshaft cylinder
  • Figure 23 is a schematic view showing the structure of US 4, 044, 629;
  • Figure 24 is a schematic view showing the structure of US 4, 073, 196.
  • the present invention provides a kinetic energy generating device, which mainly comprises a casing 1, a fixed gear 2, a movable gear 3, a transmission member 4, a flywheel 5 and a connecting rod 6.
  • the fixed gear 2 is disposed on one side of the casing 1 and has a tooth shape facing inward.
  • the movable gear 3 is disposed on the inner side of the fixed gear 2, and has a tooth shape outward, so that the fixed gear 2 and the movable gear 3 can be meshed with each other.
  • the gear ratio of the fixed gear 2 to the movable gear 3 is 3:2; and the transmission member 4 is pivoted inside the casing 1 and rotatable to connect an output shaft 43 as an engine kinetic energy output;
  • the bearing surface of the casing 1 is provided with a bearing 41 for rotation, and the transmission member 4 is inserted into the axial center of the movable gear 3 and pivotally provided with a transmission shaft 42 so that the transmission shaft 42 and the movable gear 3 are all included in the fixed gear 2
  • the axis of the movable gear 3 and the transmission shaft 42 are also provided with a bearing 44 for rotation;
  • the flywheel 5 is fixedly coupled to the outside of the movable gear 3 to rotate the flywheel 5 synchronously with the movable gear 3;
  • the flywheel 5 is provided with a force applying shaft 51.
  • the connecting rod 6 is axially disposed on the force applying shaft 51.
  • Each of the connecting rods 6 is disposed on the flywheel biasing shaft 51 except for one end shaft, and the other end is axially disposed in the cylinder.
  • the piston 7a is taken as an example, which is driven by the kinetic energy generated by the explosion in the cylinder, and is pressurized by the connecting rod 6 to the force applying shaft 51.
  • the flywheel 5 and the movable gear 3 rotate with the transmission shaft 42 as an axis.
  • the flywheel 5 and the movable gear 3 are rotated around the inner edge of the fixed gear 2, and the drive shaft 42 can be used for power output.
  • FIG. 6 to FIG. 13 have a transmission shaft 42, a force applying shaft 51, and three key points of the meshing point 9 of the fixed gear 2 and the movable gear 3; when the piston 7a explodes kinetic energy through the connecting rod
  • the inertia is simultaneously pressed by the urging shaft 51 toward the propeller shaft 42 (the urging line 01), and the reaction force of the meshing point 9 is applied to the propeller shaft 42 (the urging line) 02)
  • the output of the drive shaft 42 is much larger than the conventional structure; and the angle between the force line 01 and the force line 02 should be formed to facilitate the use of the principle of leverage to prevent the forces from canceling each other out.
  • the present invention can form a multi-cylinder, multi-angle and multi-track configuration mode.
  • the cylinder is configured as two, and each cylinder is driven by the drive shaft 42. , or 42a is a 60 ° axis configuration. Since each of the force applying shafts 51 has a separate trajectory line, it can be smoothly operated without impact, and the power of each cylinder has a multiplication effect.
  • a power stroke is completed in groups of three, as shown in the positions of the pistons 7a, 7c, and 7e in FIG. 120 ° configuration, that is, each cylinder is responsible for one-third of the kinetic energy output; when the first cylinder starts the explosion stroke, the trajectory a of the piston 7a moving between the upper and lower strokes is changed as shown in Fig. 6 to Fig. 8.
  • the inertia path produces an inertia stroke path segment s as shown in FIG. 14.
  • the inertia stroke path segment s is approximately straight, and most of the inertia of the connecting rod 6 can be applied to the movable gear 3 to rotate, reducing the lateral component force t. Loss; and when the piston 7a reaches the end of the stroke to slow down the activity, its trajectory a changes as shown in Fig. 9 and Fig. 10, the link 6 will be pushed toward the second cylinder to compress the second cylinder; The two cylinders enter the explosion stroke as shown in FIGS.
  • each power stroke of the invention is configured with three cylinders at the same time, and each cylinder sequentially explodes. That is, each explosion only rotates 120 °, its power is quite large, and the loss kinetic energy of the invention is low, so the invention can achieve the functions of low rotation speed and high torque.
  • the kinetic energy generating device of the present invention is mainly applied to an engine.
  • the present invention can also drive the drive shaft 42 to rotate by other power devices, and then power the movable gear 3, the flywheel 5, the urging shaft 51, the connecting rod 6, and finally
  • the piston 7a compresses the cylinder for energy output, that is, it is applied in the air compressor structure.
  • the air compressor needs to raise the height of the force applying shaft 51 to form a trajectory line b as shown in FIG. 15, and the kinetic energy is returned to the piston 7 for compression output energy. .
  • the number of cylinders of the present invention is designed in a multiple of three, and if the number is reduced, the balance feeling is lowered, and a vibration effect is generated, and it can also be applied to a structure such as a massage chair or a vibration device.
  • a structure such as a massage chair or a vibration device.
  • the trajectory line c formed by the height adjustment of the urging shaft 51 can be mainly seen by the user.
  • the cylinder of the present invention and its pistons 7a to 7f and the connecting rod 6 are arranged in multiples of three. As shown in the six-cylinder structure, they can be distributed into two groups, symmetrically and rotated 180. ° The angle is set at the two ends of the casing 1, and the symmetrical cylinders are subjected to the same stroke to balance and double the force to rotate the movable gear 3.
  • This structure is suitable for the vertical engine in which the cylinder is lying, so the present invention can be applied to each Vertical, horizontal engines even in air compressors.
  • the setting mode of the two urging shafts 51 is matched with the two cylinders.
  • the positions of ⁇ , ⁇ ' and ⁇ B' in the figure are the same trajectory of the cylinders on the urging shafts 51. , only deflects an angle. Therefore, in combination with the above structure, the power configuration of the present invention can be multi-cylinder, multi-angle, multi-track line mode, making it suitable for various vertical, horizontal or other engines, as well as various air compressors, massage machines, vibrations. Device, etc.
  • the transmission member 4 may be provided with a transmission gear 45.
  • the transmission shaft 42 is provided with a shaft gear 46.
  • the transmission gear 45 meshes with the shaft gear 46, so that the cylinder power is driven by the movable gear. 3 Synchronously drives the spindle gear 46 to rotate, and power transmission is performed via the transmission gear 45.
  • the number of teeth of the transmission gear 45 and the shaft gear 46 can be adjusted to vary the rotational speed to obtain the required speed and force for different purposes.
  • the transmission shaft 42 or the shaft gear 46 is pre-deflected at an angle to form an angle between the urging line 01 and the urging line 02, so that the urging line 01 and the urging line 02 produces a power superposition effect.
  • the kinetic energy generating device has three cylinders arranged at the same time for each power stroke, and each cylinder sequentially explodes, that is, each rotation only rotates 120°, and the force thereof is quite large, and the loss kinetic energy of the invention is low, so
  • the invention can achieve the functions of low rotation speed and high torque; the angle of inertia of the applied force axis is small, the oscillation and the component load loss can be reduced, and the kinetic energy output can be improved; the invention has the most configured cylinder in the limited space by the inner casing joint mode.
  • the overall output kinetic energy is greatly increased; in the present invention, the cylinder configuration can be operated separately for multi-cylinder, multi-angle, multi-track lines, and the total output force thereof is greatly increased; the kinetic energy generating device is applicable to various vertical and horizontal engines. Even air compressor structures or other power machines can be used industrially.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Transmission Devices (AREA)

Description

动能产生装置 技术领域
本发明关于一种动能产生装置， 特别是指一种在有限空间下， 减少侧向分 力损耗， 增进输出功率， 具有低转速、 高扭力， 以及减少震动的动能产生装 置。 背景技术
传统的引擎运作模式如图 22所示， 当汽缸燃烧时， 由汽缸活塞 xl推动一传 动件 x2带动曲柄轴 x3旋转以产生动能输出。 但以传动件 x2而言， 由于传动件 x2 的活动方向具有相当大的侧压角度， 故产生相当大的侧向分力， 造成整体动能 的损耗； 另外， 传统引擎在上死点时， 其施力点 x4与曲柄轴 x3的惯性力量会相 互抵消， 不仅造成动能的损耗， 更会引起震荡现象， 导致引擎损坏， 寿命减 短。
另外， 传统的引擎每一次行程必须经过进气、 压缩、 爆炸、 排气四项动 作， 此时曲柄已绕输出轴转动两圈， 即每一爆炸行程必须推动引擎输出两转， 故输出扭力较低， 因此引擎必须提高转速， 或是加大汽缸容量， 方可提供较大 的扭力给引擎使用。
坊间有许多引擎的改良方案， 如图 23所示之美国专利 US 4, 044, 629 , 其曲 柄轴 5套置在一偏心轮 8上， 该偏心轮 8则在外齿轮 7中， 当外齿轮 7啮合内齿轮 15转动时， 通过偏心轮 8可修正轴心 6的施力方向， 以提高引擎效能； 又如图 24 之美国专利 US 4， 073， 196， 其中曲柄轴 26以一悬臂 40a连接一外齿轮 43a绕行内 齿轮 44转动， 再由外齿轮轴心 37进行动能传输， 通过悬臂 40a调整轴心 37的施 力方向， 以提高引擎效能。
只是前述两件习知技术仍无法完全解决传统引擎的侧压损耗与震荡不稳的 缺点。 故其汽缸每一次爆炸仍须带动引擎输出两转， 使该引擎转速、 体积无法 缩减， 而输出的扭力仍然偏低。
由此可见， 该习知技术仍有改善空间， 本申请发明人即鉴于上述缺点， 经 由长期研究， 终研发完成本件动能产生装置， 期能提供业界更好的选择。 发明内容 本发明的主要自的即在于提供一种动能产生装置， 其爆炸行程密集， 可在 较低的转速下得到较高的输出功率， 形成低转速、 高扭力的结构。
本发明另一目的即在于提供一种动能产生装置， 其施力轴惯量角度变化较 小， 减少震荡、 分力损耗， 提高动能输出。
本发明再一目的即在于提供一种动能产生装置， 其通过内外套合方式， 在 有限空间内配置最多的汽缸， 使其整体输出动能大增。
本发明下一目的即在于提供一种动能产生装置， 其适用于各种立式、 卧式 引擎， 甚至于空压机结构或其它动力机械。
本发明又一目的即在于提供一种动能产生装置， 其汽缸配置可为多汽缸、 多角度、 多轨迹线分别运转， 使其输出总力大增。
可达成前述目的的动能产生装置， 包括有一机壳， 该机壳一侧设置有一固 定齿轮， 该固定齿轮齿形朝内， 相对在该固定齿轮内侧设置有一活动齿轮， 该 活动齿轮齿形向外， 使该固定齿轮与活动齿轮可相互啮合传动， 且该固定齿轮 与活动齿轮的齿轮比为 3 : 2 ; 另在机壳内部枢设有一传动件， 作为引擎动能输 出， 该传动件朝向活动齿轮的轴心位置穿入并枢设有一传动轴， 使该传动轴、 活动齿轮皆包含在固定齿轮的体积范围内， 而活动齿轮外侧固定连接有一飞轮 5， 使该飞轮与活动齿轮同步转动， 该飞轮一端设置有施力轴， 该施力轴上轴 设有连杆， 该连杆一端轴设在飞轮施力轴上， 其另一端则轴设在汽缸的活塞 上， 使活塞在汽缸壁上往复运动， 让活塞经由连杆带动飞轮与活动齿轮旋转， 以进行动能传输。 附图说明
请参阅以下有关本发明一较佳实施例的详细说明及其附图， 将可进一步了 解本发明的技术内容及其目的功效； 有关该实施例的附图为：
图 1为本发明的结构立体图；
图 2为本发明的结构正视图；
图 3为本发明的双汽缸配置结构侧视图；
图 4为本发明含活塞、 连杆的结构正视图；
图 5为本发明的双汽缸活动轨迹图；
图 6〜图 13为本发明的动作顺序图；
图 14为本发明的运动轨迹分析图； 图 15为本发明的施力轴高度调高轨迹分析图；
图 16为本发明的施力轴高度调低轨迹分析图；
图 17为本发明的结构变化例正视图；
图 18为本发明的结构变化例侧视图；
图 19为本发明的另一结构变化例侧视图；
图 20为本发明的另一结构变化例正视图；
图 21为本发明的传动结构变化例图；
图 22为习知曲柄轴汽缸的动作示意图；
图 23为 US 4， 044， 629的结构示意图； 以及
图 24为 US 4， 073， 196的结构示意图。
图中主要组件符号说明：
1一机壳， 2—固定齿轮， 3—活动齿轮， 4一传动件， 41 _轴承， 42、 42a 一传动轴， 43—输出轴， 44一轴承， 45—传动齿轮， 46—轴心齿轮， 5—飞 轮， 51—施力轴， 6—连杆， 7a〜7f—活塞， 9一啮合点， 01、 02—施力线， a, b，c一轨迹线， s—惯量行程区段， t一轨迹区段， xl—活塞， x2—传动件， x3—曲柄轴， x4—施力点。 最佳实施方式
请参阅图 1至图 4所示， 本发明提供一种动能产生装置， 主要包括有一机壳 1、 一固定齿轮 2、 一活动齿轮 3、 一传动件 4、 一飞轮 5与一连杆 6。
该固定齿轮 2设置在机壳 1一侧， 其齿形朝内， 该活动齿轮 3则罩设在固定 齿轮 2内侧， 其齿形向外， 使该固定齿轮 2与活动齿轮 3可相互啮合传动， 且该 固定齿轮 2与活动齿轮 3的齿轮比为 3 : 2 ; 而该传动件 4枢设在机壳 1内部并可转 动， 以连接一输出轴 43作为引擎动能输出； 该传动件 4与机壳 1接触面设置有轴 承 41以利转动， 该传动件 4朝向活动齿轮 3的轴心位置穿入并枢设有一传动轴 42， 使该传动轴 42、 活动齿轮 3皆包含在固定齿轮 2的体积范围内， 而该活动齿 轮 3的轴心与传动轴 42接触面亦设置有轴承 44以利转动； 该飞轮 5固定连接在活 动齿轮 3外侧， 使该飞轮 5与活动齿轮 3同步转动； 该飞轮 5—端设置有施力轴 51， 该连杆 6则轴设在施力轴 51上， 各连杆 6除一端轴设在飞轮施力轴 51上， 其 另一端则轴设在汽缸（图未示出）的活塞 7a〜7f上， 使活塞 7a〜7f在汽缸壁上往 复运动， 让活塞 7a〜7f经由连杆 6带动飞轮 5与活动齿轮 3旋转， 以进行动能传 输。
借助前述设计， 以该活塞 7a为例， 其由汽缸内爆炸所产生的动能带动， 经 连杆 6向施力轴 51加压， 该飞轮 5与活动齿轮 3会以传动轴 42为轴进行转动， 使 该飞轮 5与活动齿轮 3绕着固定齿轮 2内缘旋转， 该传动轴 42则可作动力输出。
而本发明的特征如图 6至图 13所示， 其具有传动轴 42、 施力轴 51 , 以及固 定齿轮 2和活动齿轮 3的啮合点 9三处关键点； 当活塞 7a爆炸动能经连杆 6加压于 施力轴 51时， 其惯量同时由施力轴 51向传动轴 42方向施压 (施力线 01)， 以及由 啮合点 9反作用力向传动轴 42方向施压（施力线 02)， 故传动轴 42输出的力量远 大于习知结构； 而该施力线 01与施力线 02之间宜形成一夹角， 以利利用杠杆原 理将力量迭加， 避免力量相互抵消。
借助前述结构， 当活塞 7a爆炸时， 其动能经连杆 6加压于施力轴 51上， 而 该连杆 6的侧压角度变化非常小， 使大部份惯量可作为推动活动齿轮 3与飞轮 5 旋转的动力， 减少侧向分力的浪费； 当活动齿轮 3绕行固定齿轮 2转动时， 该活 动齿轮 3与飞轮 5朝反方向转动， 使该施力轴 51形成如图十四轨迹线 a的形状。
通过前述对轨迹线 a的描述， 本发明可形成多汽缸、 多角度与多轨迹的配 置模式， 如图 3、 图 5、 图 14所示， 其汽缸配置为两个， 各汽缸以传动轴 42、 或 42a为轴呈 60 ° 配置， 由于各施力轴 51具有单独的轨迹线， 故运作时可平稳进 行且不会发生撞击， 且各汽缸的动力具有加乘效果。
另外， 如图 2、 图 4所示， 对于一个六汽缸引擎而言， 以三个为一组来完成 一动力行程， 如图 4中的活塞 7a、 7c、 7e位置， 各汽缸以传动轴呈 120 ° 配置， 即每一汽缸担负三分之一的动能输出； 当第一汽缸开始爆炸行程时， 其活塞 7a 在上、 下行程间活动的轨迹线 a变化如图 6至图 8所示， 此惯量路径产生如图 14 所示的惯量行程轨迹区段 s， 此惯量行程轨迹区段 s近似直线， 可将连杆 6的大 部份惯量施予活动齿轮 3转动， 减少侧向分力 t的损耗； 而当活塞 7a到达行程末 端减缓活动时， 其轨迹线 a变化如图 9、 图 10所示， 该连杆 6会偏向第二汽缸处 推进， 对第二汽缸进行压缩； 然后该第二汽缸进入爆炸行程如图 11至图 13， 使 该第二汽缸的活塞 7b对第三汽缸进行压縮， 此时第一汽缸的活塞 7a倒退以进行 排气； 如此， 当活塞 7产生最大惯量推力时， 可将大部份惯量推力施予活动齿 轮 3进行转动， 故可大幅提高本发明的动能输出。 前述活塞 7b、 7d、 7f则形成 另一动力行程， 其轨迹线与 7a、 7c、 7e相差 60° 角度。
再者， 传统引擎必须进行进气、 压缩、 爆炸、 排气四项动作来完成一次行 程， 即引擎每输出一转仅为 1/2次爆炸的力量， 故引擎转速要更快， 且输出扭 力较低； 而本发明每一动力行程同时配置三个汽缸， 各汽缸依序进行爆炸， 即 每次爆炸仅转动 120 ° ， 其力量相当庞大， 加上本发明损失动能较低， 故本发 明可达到低转速、 高扭力的功能。
另外， 本发明动能产生装置， 主要应用在引擎中， 反之， 本发明亦可由其 它动力装置推动传动轴 42旋转， 再将动力经由活动齿轮 3、 飞轮 5、 施力轴 51、 连杆 6， 最后由活塞 7a压缩汽缸进行能量输出， 即应用在空压机结构中， 此空 压机需调高施力轴 51高度， 形成如图 15的轨迹线 b， 让动能输回活塞 7进行压缩 输出能量。 又， 本发明的汽缸数以三的倍数量设计， 若减少其数量， 使其平衡 感下降， 则会产生震动效果， 亦可应用在按摩椅或震动装置等结构中。 当然， 亦可如图 16所示因施力轴 51高度调低形成的轨迹线 c， 主要是看使用者需要。
请参阅图 17、 图 18所示， 本发明的汽缸以及其活塞 7a〜7f、 连杆 6是以三 的倍数设置， 如图所示的六汽缸结构， 可分配成两组， 对称并转动 180 ° 角设 置在机壳 1两端， 并使相对称的汽缸进行相同的行程， 以平衡并加倍力量旋转 活动齿轮 3， 此结构适用于汽缸平躺的立式引擎， 故本发明可适用于各种立 式、 卧式引擎甚至于空压机中。
另请参阅图 19、 图 20所示， 为单一施力轴 51配合两个汽缸的设置模式， 如 图中 Α、 Α' 与^ B' 的位置， 各施力轴 51上的汽缸为同一轨迹， 仅偏转一角 度。 因此， 综合以上结构， 本发明的动力配置可为多汽缸、 多角度、 多轨迹线 方式， 使其适用在各种立式、 卧式或其它引擎， 以及各种空压机、 按摩机、 震 动装置等。
又如图 21所示， 其中该传动件 4可设置有传动齿轮 45， 该传动轴 42则设有 轴心齿轮 46， 该传动齿轮 45与轴心齿轮 46啮合传动， 故汽缸动力是由活动齿轮 3同步带动轴心齿轮 46旋转， 经由传动齿轮 45进行动力传输。 而该传动齿轮 45 与轴心齿轮 46的齿数可以调整， 以变化转动速度， 借以得到所需的速度与力 量， 以适合不同的使用目的。
前述活塞 7a位于行程始点时， 该传动轴 42或轴心齿轮 46得预先偏转有一角 度， 使该施力线 01与施力线 02之间形成一夹角， 使施力线 01与施力线 02产生力 量迭加效果。
以上对本发明一可行实施例进行了具体说明， 该实施例并非用以限制本发 明的保护范围， 凡未脱离本发明技艺精神所为的等效实施或变更， 均应包含于 本发明中。 工业应用性
本发明提供的动能产生装置， 每一动力行程同时配置三个汽缸， 各汽缸依 序进行爆炸， 即每次爆炸仅转动 120 ° ， 其力量相当庞大， 加上本发明损失动 能较低， 故本发明可达到低转速、 高扭力的功能； 其施力轴惯量角度变化较 小， 可减少震荡、 分力损耗， 提高动能输出； 本发明其通过内外套合方式， 在 有限空间内配置最多的汽缸， 使其整体输出动能大增； 本发明中汽缸配置可 为多汽缸、 多角度、 多轨迹线分别运转， 使其输出总力大增； 该动能产生装置 适用于各种立式、 卧式引擎， 甚至于空压机结构或其它动力机械， 能够在工业 上应用。

Claims

权利要求
1. 一种动能产生装置， 包括有一机壳、 一固定齿轮、 一活动齿轮、 一传 动件、 一飞轮与一连杆， 其特征在于：
该固定齿轮设置在机壳一侧， 其齿形向内； 该活动齿轮罩设在固定齿轮内 侧， 其齿形向外， 并使该固定齿轮与活动齿轮啮合传动， 且该固定齿轮与活动 齿轮的齿轮比为 3 : 2 ; 该传动件枢设在机壳内部而可转动， 该传动件朝向活动 齿轮的轴心位置穿入并枢设有一传动轴， 使该传动轴、 活动齿轮皆包含在固定 齿轮的体积范围内； 该飞轮固定连接在活动齿轮外侧， 该飞轮一端设置有施力 轴， 该连杆则轴设在施力轴上， 各连杆除一端轴设在飞轮施力轴上， 其另一端 则轴设在汽缸的活塞上； 据此， 该施力轴运动的轨迹线侧压角度变化非常小， 减少侧向分力的浪费。
2. 如权利要求 1所述的动能产生装置， 其特征在于： 其中该汽缸数为三的 倍数， 并以每三个为一组并排设置， 且每一组的三个汽缸互呈 120° 的角度配 置。
3. 如权利要求 1所述的动能产生装置， 其特征在于： 其中该汽缸数为三的 倍数， 并以每三个为一组并排设置， 且每一组的三个汽缸可呈多种角度配置。
4. 如权利要求 1所述的动能产生装置， 其特征在于： '其中每一轨迹的汽缸 数可同时配置多数个， 使各汽缸具有独立的动力轨迹行程。
5. 如权利要求 1所述的动能产生装置， 其特征在于： 其中每一动力行程的 施力轴上的汽缸数可同时配置多数个， 并分配在同一轨迹线的不同角度位置。
6. 如权利要求 1所述的动能产生装置， 其特征在于： 其中该活塞位于行程 始点时， 该传动轴预先偏转有一角度。
7. 如权利要求 1所述的动能产生装置， 其特征在于： 其中该施力轴高度可 调整， 以改变轨迹线， 并适用于各种动力装置。
8. 如权利要求 1所述的动能产生装置， 其特征在于： 其中该传动件设置有 传动齿轮， 该传动轴则设有轴心齿轮， 通过传动齿轮与轴心齿轮啮合以传输动 力。
9. 如权利要求 8所述的动能产生装置， 其特征在于： 其中该传动齿轮与轴 心齿轮的齿数可以调整， 以变化转动速度。
PCT/CN2006/002106 2006-08-18 2006-08-18 Appareil de transmission d'énergie cinétique Ceased WO2008022489A1 (fr)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5158047A (en) * 1990-05-14 1992-10-27 Schaal Jack E Delayed drop power stroke internal combustion engine
US5170757A (en) * 1991-12-24 1992-12-15 Damien Gamache Variable horsepower output gearing for piston engine
DE19505467A1 (de) * 1995-02-02 1996-08-22 Chiou Chui Cy Kolben-Zylinderanordnung
WO1997026452A1 (en) * 1996-01-19 1997-07-24 Peter Robert Raffaele Three cycle engine
WO1998048158A1 (en) * 1997-04-21 1998-10-29 Peter Robert Raffaele Three cycle engine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5158047A (en) * 1990-05-14 1992-10-27 Schaal Jack E Delayed drop power stroke internal combustion engine
US5170757A (en) * 1991-12-24 1992-12-15 Damien Gamache Variable horsepower output gearing for piston engine
DE19505467A1 (de) * 1995-02-02 1996-08-22 Chiou Chui Cy Kolben-Zylinderanordnung
WO1997026452A1 (en) * 1996-01-19 1997-07-24 Peter Robert Raffaele Three cycle engine
WO1998048158A1 (en) * 1997-04-21 1998-10-29 Peter Robert Raffaele Three cycle engine

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