WO1999046507A1 - Compresseur a gaz de type a dents complexes - Google Patents

Compresseur a gaz de type a dents complexes Download PDF

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Publication number
WO1999046507A1
WO1999046507A1 PCT/CN1998/000322 CN9800322W WO9946507A1 WO 1999046507 A1 WO1999046507 A1 WO 1999046507A1 CN 9800322 W CN9800322 W CN 9800322W WO 9946507 A1 WO9946507 A1 WO 9946507A1
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WO
WIPO (PCT)
Prior art keywords
gear
teeth
tooth
exhaust
driven gear
Prior art date
Application number
PCT/CN1998/000322
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English (en)
French (fr)
Inventor
Jinfeng Shen
Rongfu Liu
Jicheng Liu
Jun Wang
Original Assignee
Osen Science & Technology Co., Ltd.
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Osen Science & Technology Co., Ltd. filed Critical Osen Science & Technology Co., Ltd.
Priority to AU17476/99A priority Critical patent/AU1747699A/en
Priority to EP98962170A priority patent/EP1063429A4/en
Priority to JP2000535848A priority patent/JP2002506173A/ja
Priority to US09/623,644 priority patent/US6352420B1/en
Publication of WO1999046507A1 publication Critical patent/WO1999046507A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/20—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with dissimilar tooth forms

Definitions

  • the invention relates to a composite gear-tooth type gas compressor. Background technique
  • United States patent document US3 574 491 discloses a compound gear-tooth rotary machine which can be used for conveying liquid, compressed or expanded gas, which has: a housing which defines an inner cavity and is provided with an air inlet hole and An exhaust hole; a pair of intermeshing gears installed in the housing, each gear includes two sets of gear teeth of different sizes with a common indexing circle, a pair of shafts, each shaft is rotatably mounted on the housing and One of the above-mentioned gears is fixedly mounted thereon.
  • a torque transmitting device for driving the pair of gears is mounted on the pair of shafts outside the casing, so that the pair of gears do not actually touch each other during the turning process. .
  • the known rotary machine has a large volume and a complicated structure because the torque transmission device is added. Moreover, because the gears are not in contact with each other, especially the large teeth are in the form of a meshing structure with a unit of one cycle (one tooth and one groove), a large amount of liquid will flow back, which is very inefficient, and basically does not have the function of compressing and expanding gas . This rotary machine is difficult to achieve industrial applications. Summary of the Invention
  • the object of the present invention is to provide a composite gear-tooth type gas compressor with low noise, small volume, simple structure, and reduced or avoided return air charging.
  • the present invention provides such a composite gear-tooth type gas compressor, which has: a casing and two upper and lower end covers respectively installed on both sides of the casing, which form a closed space; two Intermeshing gears rotatably located in the above-mentioned enclosed space, each of which includes two kinds of teeth of different sizes having a common indexing circle; an air inlet hole and an exhaust hole; and an air inlet in the enclosed space A suction cavity on the hole side; and a pressure exhaust cavity on the exhaust hole side in a closed space; wherein: one of the above-mentioned gears is a driving gear with large teeth thereon, and the other gear is a driven gear on which There is a large cogging corresponding to the above-mentioned large tooth; the above-mentioned gear rotates unidirectionally; both the above-mentioned large tooth and the large-tooth slot are asymmetrical tooth shapes; The front tooth profile curves of the large teeth and the large tooth grooves are
  • an exhaust hole is provided on the above-mentioned end cover, and a clearance exhaust groove which can communicate the large tooth groove and the exhaust hole is provided on the gear with a large tooth groove.
  • the transmission mechanism and gas compression mechanism are combined into one, and the structure is particularly simple. There are only five main parts of the whole machine: a pair of gears, a housing, and upper and lower end covers, which are light in weight, small in size, and low in cost.
  • FIG. 1 is a momentary state diagram of a composite gear tooth mechanism with large teeth and large coggings designed symmetrically;
  • FIG. 2 is another instantaneous state diagram of the composite gear tooth mechanism in which the large teeth and the large teeth are symmetrically designed;
  • Figure 3 shows one of the instantaneous states of rotation of a compound gear mechanism with a large tooth and a large cogging
  • Figure 4 shows the second instantaneous state of rotation of a compound gear mechanism with large teeth and large coggings
  • Figure 5 shows the third state of the instantaneous rotation of the compound gear mechanism with asymmetric gears and large teeth
  • FIG. 6 is a curve diagram of a large tooth profile in the present invention 7 is an example of a tooth profile curve of a large cogging corresponding to FIG. 6;
  • Figure 8 is an example of a large tooth profile curve
  • FIG. 9 is an example of a tooth profile curve of a large cogging corresponding to FIG. 8; FIG.
  • FIG. 10 is a schematic diagram of another design of the compound gear mechanism of the present invention.
  • FIG. 11 is a schematic structural diagram of an air-conditioning compressor using the composite gear tooth mechanism of the present invention. Best Mode of the Invention
  • Figures 1 and 2 show a compound gear mechanism for an air compressor.
  • the composite gear tooth mechanism is installed in a closed space composed of a housing 1 and two end covers 2, 3 respectively mounted on both sides of the housing 1.
  • the mechanism includes a driving gear 21 and a driven gear 22 meshing with the driving gear.
  • the driving gear 21 and the driven gear 22 each have two types of gear teeth, and the two types of gear teeth have a common indexing circle.
  • a suction chamber 6 and a discharge chamber 7 are formed between the housing 1 and the gear.
  • the gas compressor has an air inlet hole 4 and an air outlet hole 5, in particular, the air outlet hole 5 is provided on the end cover 2.
  • the driving gear 21 has a complete large tooth
  • the driven gear 22 has a large cogging corresponding to the large tooth.
  • the large teeth on the driving gear 21 and the large teeth on the driven gear 22 are symmetrical.
  • Figures 3-5 show the three instantaneous states of rotation of a compound gear mechanism with large teeth and large coggings that are asymmetric.
  • the high-pressure gas in the pressure-exhaust cavity 7 has just communicated with the large cogging, and at the same time, the large-cogging gas also communicates with the exhaust hole 5, and the high-pressure gas starts to be discharged from the exhaust hole 5.
  • the compound gear mechanism continues to rotate to the state shown in FIG. 4
  • the high-pressure gas is pressed into the large tooth groove and continues to exhaust, at the same time the large tooth tooth back contacts the large tooth groove profile, and the next compression process starts. At this time, the contact between the large tooth back and the large tooth groove profile can prevent high pressure gas from flowing back and inflated.
  • the curves 17 and 24 in Figures 6 and 7 are designed according to the constant speed ratio required by the gear transmission, which can be involute or cycloid.
  • the curve 26 is realized by cycloid.
  • Curves 14 and 30 are also realized by cycloids. From point 15 to point 13, there can always be a little continuous contact with each other to ensure tightness and avoid high-pressure gas backflow. Points 31 and 15 start to mesh when the large teeth leave the pressure exhaust cavity 7. .
  • the top tooth width is equal to the bottom tooth width d.
  • Curve 12 is the transition line, which is determined by the motion trajectory of point 31, and smoothly transitions with the small tooth root circle (at point 11). Points 13 and 25 also transition smoothly from small arcs.
  • Figures 8 and 9 show a pair of examples of tooth profile curves for large teeth and large coggings.
  • the data at each point in the figure is the coordinate value of that point.
  • Figure 10 shows a schematic diagram of a gas compressor with two driven gears. It can be seen from FIG. 10 that the gas compressor has two air inlet holes 4 and two air outlet holes 5. Compared with a gas compressor with only one driven gear, the gas compressor doubles its displacement.
  • FIG. 11 is a schematic diagram of an air-conditioning compressor designed using the compound gear mechanism of the present invention.
  • the motor 11 and the compressor are both installed in a sealed casing 10, and the compressor is located below the motor 11.
  • the air inlet hole 4 of the compressor is located on the casing 1 of the compressor, and the air outlet hole 5 is located on the upper end cover 2.
  • a closed space is formed by the casing 1, the upper end cover 2 and the lower end cover 3, and a compound gear mechanism composed of a driving gear and a driven gear is installed in the closed space.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Description

复合轮齿式气体压缩机 技术领域
本发明涉及一种复合轮齿式气体压缩机。 背景技术
美国专利文件 US3 574 491公开了一种可用于输送液体、 压缩或膨 胀气体的复合轮齿式回转机械， 它具有： 一个壳体， 该壳体限定出一个 内腔并设有一个进气孔和一个排气孔； 一对装入壳体内的相互啮合的齿 轮， 每个齿轮均包括两组具有公共分度圓的不同尺寸的轮齿， 一对轴， 每个轴旋转安装于壳体上并在其上固定安装上述齿轮之一。 根据该已知 的回转机械， 在壳体之外在上述一对轴上安装有用于驱动上述一对齿轮 的扭矩传递装置， 从而使上述一对齿轮在回转过程中实际上相互之间并 不接触。 该已知的回转机械由于附加了上述扭矩传递装置使其体积较 大， 结构复杂。 而且， 由于齿轮互不接触， 特别是大齿是以周节为单元 (一齿一槽） 的啮合结构形式， 输送液体会发生大量回流， 效率很低， 基本上不具有压缩和膨胀气体的功能。 该回转机械难以实现工业应用。 发明内容
本发明的目的是提供一种噪声小、 体积小、 结构简单同时使回流充 气减少或避免的复合轮齿式气体压缩机。
为达到上述目的， 本发明提供这样一种复合轮齿式气体压缩机， 它 具有： 一个壳体和两个分别安装于该壳体两侧的上、 下端盖， 它们构成 一密闭空间； 两个可转动地位于上述密闭空间内的相互啮合的齿轮， 每 个齿轮均包括两种具有公共分度圆的不同尺寸的轮齿； 一个进气孔和一 个排气孔； 在密闭空间内位于进气孔侧的抽吸腔； 以及， 在密闭空间内 位于排气孔侧的压排腔； 其中： 上述齿轮之一为主动齿轮， 其上有大齿， 而另一个齿轮为从动齿轮， 其上有与上述大齿对应的大齿槽； 上述齿轮 是单向转动的； 上述大齿和大齿槽均为不对称齿形； 沿旋转方向看， 上 述大齿和大齿槽的前齿廓曲线设计成实现定角速比传动， 而它们的后齿 廓曲线设计成在其开始接触至其最终分离期间始终共轭接触。
按本发明的进一步设计， 排气孔设于上述端盖上， 在有大齿槽的齿 轮上设有可连通大齿槽与排气孔的余隙排气槽。
按本发明的复合轮齿式气体压缩机具有下述优点：
1. 传动机构与气体压缩机构合而为一， 结构特别简单， 全机主要零 件只有五个： 一对齿轮、 壳体和上、 下端盖， 其重量轻、 体积小、 成本 低。
2. 动平衡性能良好， 无曲柄或偏心机构， 运动平稳， 振动小， 无须 进、 排气阀， 噪声低。
3. 齿廓曲线的不对称设计和余隙排气槽的设置， 使余隙容积小， 避 免了回流充气现象， 同时机械磨损小， 所以能效比和容积效率较高。
附图概述
通过下面结合附图对优选实施例的描述， 会更好地理解本发明。 附 图中：
图 1为大齿和大齿槽均为对称设计的复合轮齿机构的一个旋转瞬时 状态图；
图 2为大齿和大齿槽均为对称设计的复合轮齿机构的另一个旋转瞬 时状态图；
图 3表示大齿和大齿槽均为非对称设计的复合轮齿机构的旋转瞬时 状态之一；
图 4表示大齿和大齿槽均为非对称设计的复合轮齿机构的旋转瞬时 状态之二；
图 5表示大齿和大齿槽均为非对称设计的复合轮齿机构的旋转瞬时 状态之三；
图 6是本发明中的大齿齿廓曲线图 图 7是与图 6对应的大齿槽齿廓曲线的实例；
图 8是大齿齿廓曲线的一个实例；
图 9是与图 8对应的大齿槽齿廓曲线的一个实例；
图 10是本发明的复合轮齿机构的另一种设计的示意图；
图 1 1是采用本发明的复合轮齿机构的空调压缩机的结构示意图。 本发明的最佳实施方式
图 1和 2示出了一种用于空气压缩机的复合轮齿机构。 该复合轮齿 机构装在由壳体 1和两个分别安装于壳体 1两侧上的端盖 2、 3构成的 密闭空间内。该机构包括一个主动齿轮 21和一个与主动齿轮啮合的从动 齿轮 22。 主动齿轮 21和从动齿轮 22均具有两种轮齿， 两种轮齿具有公 共的分度圓。 如图 1和 2所示， 在壳体 1与齿轮之间形成有一个抽吸腔 6和一个压排腔 7。 该气体压缩机具有进气孔 4和排气孔 5 , 特别是， 排气孔 5设于端盖 2上。 需要说明的是， 主动齿轮 21具有完整的大齿， 而从动齿轮 22具有与上述大齿对应的大齿槽。 主动齿轮 21上的大齿和 从动齿轮 22 上的大齿槽均是对称形的。 当该复合轮齿机构旋转到图 1 所示位置时， 齿背出现间隙， 造成已被排至大齿槽内的部分高压气体将 顺着大齿齿背回流至压排腔 7内。 当该复合轮齿机构旋转到图 2所示状 态时， 残留于大齿槽余隙 8中的高压气体无法进入排气孔 5 , 并最终将 进入抽吸腔 6中造成能量损失， 影响进气量， 甚至出现噪声。
图 3 ― 5分别表示大齿和大齿槽均为非对称形的复合轮齿机构的三 个旋转瞬时状态。 在图 3所示状态， 压排腔 7内的高压气体刚与大齿槽 连通， 与此同时， 大齿槽也与排气孔 5连通， 高压气体开始从排气孔 5 排出。 当复合轮齿机构继续旋转至图 4所示状态时， 高压气体被压入大 齿槽内并继续排气， 与此同时大齿齿背与大齿槽齿廓接触， 下一次压缩 过程开始。 这时， 大齿齿背与大齿槽齿廓的接触可以防止高压气体回流 充气。 当复合轮齿机构继续旋转至图 5所示的状态时， 大齿槽与排气孔 5失去直接连通， 为了避免余隙 8中存在的高压气体重新回到低压的抽 吸腔 6中， 在齿轮的端面上开有使余隙 8与排气孔 5相连通的余隙排气 槽 9 : 使余隙 8中的高压气体经余隙排气槽 9排入排气孔 5中。 图 6和 7给出了大齿及大齿槽的齿廓曲线。 从图 6和 7可以看出， 大齿及大齿槽的齿廓曲线是非对称形的， 其设计目的是为了防止高压气 体回流充气和尽量减少余隙容积。 考虑到在压缩机中各齿轮是单向转动 的， 图 6和 7中的曲线 17和 24按齿轮传动要求的定速比设计， 其可为 渐开线或摆线。 当曲线 17和 24脱离而后续小齿还没有进入啮合时， 此 时转动由曲线 17和 1曲线 26完成。 根据啮合原理， 利用解析法采用计 算机设计分析并考虑加工方便， 曲线 26用摆线来实现。 曲线 14与曲线 30也由摆线实现， 从点 15至点 13始终相互能连续有一点接触， 以保证 密闭， 避免高压气体回流， 点 31与点 15在大齿脱离压排腔 7时开始啮 合。 大齿顶宽与大齿槽底宽 d相等。 曲线 12为过渡线， 它由点 31的运 动轨迹决定， 并与小齿齿根圆（点 11处）光滑过渡。 点 13和点 25处也 由小圆弧光滑过渡。
图 8和图 9给出了大齿和大齿槽的齿廓曲线的一对实例， 图中每点 的数据是该点的坐标值。
图 10给出了有两个从动齿轮的气体压缩机的示意图。 从图 10中可 以看出， 该气体压缩机具有有两个进气孔 4 , 两个排气孔 5。 该气体压 缩机与只有一个从动齿轮的气体压缩机相比， 排量增加了一倍。
图 11 给出了采用本发明的复合齿轮机构设计的空调压缩机的示意 图。 图中电机 11和压缩机均装于密闭的机壳 10内， 且压缩机位于电机 11下面。 压缩机的进气孔 4位于压缩机的壳体 1上， 排气孔 5位于上端 盖 2上。 由壳体 1、 上端盖 2和下端盖 3形成一密闭空间， 由一个主动 齿轮和一个从动齿轮构成的复合轮齿机构装于此密闭空间内。 结合图 3 可知， 当电机帶动主动齿轮转动时， 抽吸腔 6的容积逐渐增大， 形成局 部负压， 气体经进气孔 4吸入抽吸腔 6。 随着齿轮的转动， 气体被带到 压排腔 7 , 且压排腔 7的容积逐渐减小， 气体被压缩。 当齿轮转动到压 排腔 7与排气孔 5直接连通时， 气体被压出。 齿轮继续啮合转动， 余隙 8中的气体最后通过余隙排气槽 9排向上端盖 1上的排气孔 5。 齿轮不 断地啮合转动， 就连续不断地实现了压缩机的基本工作过程—吸气、 输 送、 压缩和排气。 经压缩机排出的气体被集中于机壳 10内的上部空腔， 并最终被排至工作回路,

Claims

权 利 要 求
1. 一种复合轮齿式气体压缩机， 它具有： 一个壳体和两个分别安装于该 壳体两侧的上、 下端盖， 它们构成一密闭空间； 两个可转动地位于上述 密闭空间内的相互啮合的齿轮， 每个齿轮均包括两种具有公共分度圆的 不同尺寸的轮齿； 一个进气孔和一个排气孔； 在密闭空间内位于进气孔 侧的抽吸腔； 以及， 在密闭空间内位于排气孔侧的压排腔； 其特征在于： 上述齿轮之一为主动齿轮， 其上有大齿， 而另一个齿轮为从动齿轮， 其 上有与上述大齿对应的大齿槽； 上述齿轮是单向转动的； 上述大齿和大 齿槽均为不对称齿形； 沿旋转方向看， 上述大齿和大齿槽的前齿廓曲线 设计成实现定角速比传动， 而它们的后齿廓曲线设计成在其开始接触至 其最终分离期间始终共轭接触。
2. 如权利要求 1所述的复合轮齿式气体压缩机， 其特征在于： 上述排气 孔设于上述端盖上； 从动齿轮的端面上设有可连通大齿槽与排气孔的余 隙排气槽。
3. 如权利要求 1所述的复合轮齿式气体压缩机， 其特征在于， 它还包括 至少一个与上述主动齿轮啮合的从动齿轮； 以及， 为每个从动齿轮， 各 配设一个进气孔和一个排气孔。
PCT/CN1998/000322 1998-03-11 1998-12-31 Compresseur a gaz de type a dents complexes WO1999046507A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
AU17476/99A AU1747699A (en) 1998-03-11 1998-12-31 A complex teeth-type gas compressor
EP98962170A EP1063429A4 (en) 1998-03-11 1998-12-31 COMPLEX TEETH TYPE GAS COMPRESSOR
JP2000535848A JP2002506173A (ja) 1998-03-11 1998-12-31 複合歯形気体圧縮機
US09/623,644 US6352420B1 (en) 1998-03-11 1998-12-31 Complex teeth-type gas compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN98111890A CN1058773C (zh) 1998-03-11 1998-03-11 复合轮齿式气体压缩机
CN98111890.9 1998-03-11

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WO1999046507A1 true WO1999046507A1 (fr) 1999-09-16

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PCT/CN1998/000322 WO1999046507A1 (fr) 1998-03-11 1998-12-31 Compresseur a gaz de type a dents complexes

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EP (1) EP1063429A4 (zh)
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WO (1) WO1999046507A1 (zh)

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EP1195541A1 (en) * 1999-06-14 2002-04-10 Wei Xiong A gear and a fluid machine with a pair of gears

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US7841082B2 (en) * 2002-05-06 2010-11-30 Lurtz Jerome R Non-eccentric devices
US8291722B2 (en) * 2002-05-06 2012-10-23 Lurtz Jerome R Generator using gravitational and geothermal energy
US7201134B2 (en) * 2005-03-09 2007-04-10 Aaron Matthew Guest Parallel rotary engine
DE102007019958B4 (de) * 2006-08-14 2011-11-10 Ralf Hettrich Vielzahndrehkolbenmotor mit extrem hohen Drehmoment bei niedrigsten als auch bei sehr hohen Drehzahlen wie in Bereichen einer Turbine, als Antrieb oder zum Einsatz der Energiegewinnung, Energieumwandlung oder Energierückgewinnung
JP2008051086A (ja) * 2006-08-22 2008-03-06 Yoshinori Shinohara 気密構造ギヤーボックス状装置及びその利用方法
US20080181803A1 (en) * 2007-01-26 2008-07-31 Weinbrecht John F Reflux gas compressor
US8794945B2 (en) * 2008-04-10 2014-08-05 Fritz Forgy Rotary pump or motor with orbital piston aspiration
WO2013137337A1 (ja) * 2012-03-14 2013-09-19 国立大学法人名古屋工業大学 ローター・セット、内燃機関、流体ポンプ、流体圧縮機、および機械
WO2014032120A1 (en) * 2012-09-03 2014-03-06 Bill Yang Gear assembly
CN103967599A (zh) * 2014-05-23 2014-08-06 于临涛 双推旋转发动机
CN108678949A (zh) * 2018-05-14 2018-10-19 候永生 凹凸齿、轮式空气压缩机、泵
US20220120133A1 (en) * 2019-07-12 2022-04-21 Leafy Windoware Co., Ltd. Curtain cord retracting and releasing device and transmission mechanism thereof
CN110259690B (zh) * 2019-07-24 2024-01-02 中国石油大学(华东) 一种复合轮齿压缩机的排气口及其设计方法

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DE3324485A1 (de) * 1983-07-07 1985-01-24 Josef 6100 Darmstadt Pruner Als zahnradmotor oder als zahnradpumpe geeignete maschine
WO1991002888A1 (en) * 1989-08-22 1991-03-07 Michel Kozoubsky Rotating internal combustion engine
EP0432287A1 (en) * 1989-11-28 1991-06-19 Waldemar H. Kurherr Rotary engine
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Cited By (3)

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Publication number Priority date Publication date Assignee Title
EP1195541A1 (en) * 1999-06-14 2002-04-10 Wei Xiong A gear and a fluid machine with a pair of gears
US6709250B1 (en) 1999-06-14 2004-03-23 Wei Xiong Gear and a fluid machine with a pair of gears
EP1195541A4 (en) * 1999-06-14 2004-05-19 Wei Xiong GEAR AND APPARATUS FOR DOUBLE GEAR FLUID

Also Published As

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AU1747699A (en) 1999-09-27
CN1058773C (zh) 2000-11-22
EP1063429A4 (en) 2004-05-06
EP1063429A1 (en) 2000-12-27
CN1191940A (zh) 1998-09-02
US6352420B1 (en) 2002-03-05
JP2002506173A (ja) 2002-02-26

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