^284182 九、發明說明： 【發明所屬之技術領域】 本發明係有關於一種二級行星齒輪減速機構，尤指一 種可將引擎動力源端輸入之高速低扭力軸功馬力轉換成低 速高扭力之輸出軸功馬力之減速機構，其第二級之太陽齒 直接與第一級内環齒聯接成一體之兩級減速齒輪組搭配方 式較傳統技術更具低製造成本之經濟價值並可縮減體積， 鲁 其隱藏式油道設計可同時提供液靜壓軸承及齒間運轉潤滑 所需，再者，其行星式齒輪箱結構因輸出、入轴為同軸線， 較傳統平行轴配置方式之齒輪箱節省使用空間，而其高 速、高負載靜屋轴承具特殊之錫基軸承合金之配方，可提 供軸承高耐磨、耐壓、抗腐蝕及耐疲勞強度之性能。 【先前技術】 目前被機械業界廣泛應用之行星齒輪，其作用主要用 於減機構，其基本架構可參考美國專利4,656,891美國 專利 Planetary gear box With two double eccentrics」 或美國專利 4,986,802 美國專利 r pianetary gearb〇x f〇r a甘=ck」之内容’―般而言，運用行星齒輪之減速機構， ^本^必彡m域錄，於太料輪外環繞樓合 1<而=齒輪，藉此多級齒輪設置，可達到減速之目的， 星齒輪減速機構所普遍存在之缺點在於，其各 再5车U系串聯使用，其結構複雜、體積龐大且佔空間; ’ t件必須承受高轉速、高負載，因此對於潤滑性 1284182 能要求甚高，尤其承載齒輪之軸承，必須設定油路系統以 提供潤滑，因此造成潤滑油路系統之複雜化。 【發明内容】 有鑑於前項習知技術之缺失，本發明之主要目的在於 提出一種可將引擎動力源端輸入之高速低扭力軸功馬力轉 換成低速高扭力之輸出軸功馬力之二級行星齒輪減速機 構，其採用兩級減速齒輪組搭配方式較傳統技術更具低製 • 造成本之經濟價值。 本發明之次要目的在於提出一種二級行星齒輪減速機 構，其第二級之太陽齒直接與第一級内環齒聯接成一體之 兩級減速齒輪組搭配方式較傳統技術更具低製造成本之經 濟價值並可縮減體積。 本發明之另一目的在於提出一種二級行星齒輪減速機 構，其隱藏式油道設計可同時提供液靜壓軸承及齒間運轉 潤滑所需。 • 本發明之再一目的在於提出一種二級行星齒輪減速機 構，其行星式齒輪箱結構因輸出、入軸為同軸線，較傳統 平行軸配置方式之齒輪箱節省使用空間 本發明之又一目的在於提出一種二級行星齒輪減速機 構，其高速、高負載靜壓軸承具特殊之錫基軸承合金之配 • 方，可提供軸承高耐磨、耐壓、抗腐蝕及耐疲勞強度之性 -能。 為達到上述目的，本發明提出一種二級行星齒輪減速 :1284182 I 機構，一種二級行星齒輪減速機構，其包含： ^ 一第一級齒輪組’其具有一馬力輸入軸，用以輸入高 速低扭力軸功馬力，該馬力輸入軸軸接一太陽齒輪嚅合複 數之行星齒輪，該複數之行星齒輪並嚅合於一内環齒輪 内，該内環齒輪設有一齒輪軸，該齒輪軸上之一端設有外 齒； 一第二級齒輪組，其具有一馬力輸出軸，用以輸出低 速高扭力軸功馬力，該馬力輸出軸設有複數之行星齒輪， • 該複數之行星齒輪係與前述第一級齒輪組之齒輪軸上之外 齒相灌合。 較佳地，該第一級齒輪組之複數之行星齒輪係設置於 一固定式托板上，該第二級齒輪組之複數之行星齒輪係設 置於一連接馬力輸出軸之法蘭（Flange)上，該固定托板及 馬力輸出軸法蘭均具有複數之油道，該油道之一端係通往 外部油管，另一端則連通該複數之行星齒輪。 較佳地，該行星齒輪係包含： • -外環齒輪； 一靜壓軸承，係軸設於外環齒輪内，具有徑向貫通軸 承中心之油道，且於靜壓軸承外侧壁設有凹槽連通該油道； 一固定銷，係軸設於靜壓軸承内及托板上，該固定銷 與靜壓軸承之間具有油道，該油道並與前述靜壓軸承之徑 向油道連通； - 該托板之油道則與該固定銷與靜壓軸承間之油道，以 及靜壓軸承之徑向油道連通形成通路。 《1284182 y 較佳地，該靜壓軸承係具為錫基合金。 ' 較佳地，該錫基合金主要係以86〜90%錫、2. 7〜3. 5%銅、 - · 6〜7. 5%録與其他金屬之比例構成。 較佳地，該固定銷與靜壓軸承之間具有一間隙，該間 隙係連通托板之油道； 該靜壓軸承外側壁之凹槽使靜壓軸承外側壁與外環齒 輪内側壁形成一間隙； 該靜歷軸承具有至少一徑向貫通靜壓軸承本體之油 道，該油道之一端與前述靜壓軸承外側壁所設之凹槽連通。 較佳地，該第一級齒輪組及該第二級齒輪組托板均具 有複數之油道，該複數之油道具有複數通孔，部分通孔朝 向靜壓軸承，部分通孔則朝向行星齒輪間。 較佳地，該第二級齒輪組之馬力輸出軸内設有一軸向 封閉式凹槽構成儲油室，該儲油室連通複數之徑向貫通馬 力輸出軸之油道，以及複數之斜向貫通馬力輸出軸法蘭之 I 通往行星齒輪之通孔，該馬力輸出軸内儲油室與外部油管 之間設置有一連接件，讓連接件包括： 一襯環，係固設於齒輪箱殼内孔上，談齒輪箱殼係供 外部油管穿設，該襯環具有一内環形油道用以承接外部油 管提供之潤滑油通過，於固定之襯環與馬力輸出軸之間設 有一轴承； ， 一軸套，係套設於馬力輸出軸外，其與上述襯環之間 - 設有一軸承，該軸套具有一貫通之油孔，該油孔之一端可 連通襯環之内環形油道，另一端則固接於連通徑向貫通馬 :1284182 -„ *- 力輸出轴之油道、 • 該軸套、馬力輸出軸、軸承内環係呈干涉配合，可一 體同步轉動，而談固定襯環與軸套之間具有一間隙，使得 軸套隨馬力輸出軸同步轉動時不致對固定襯環形成干涉。 為使貴審查委員對於本發明之結構目的和功效有更 進一步之了解與認同，茲配合圖示詳細說明如后。 【實施方式】 以下將參照隨附之圖式來描述本發明為達成目的所使 用的技術手段與功效，而以下圖式所列舉之實施例僅為輔 助說明，以利貴審查委員暸解，但本案之技術手段並不限 於所列舉圖式。 請參閱圖一至圖三所示，本發明所提供之二級行星齒 輪減速機構，其係由圖一所示之第一級齒輪組10，以及圖 二所示之第二級齒輪組20所構成；該第一級齒輪組10， 其具有一用以輸入高速低扭力軸功馬力之馬力輸入軸11， 於該馬力輸入軸11軸設並驅動一太陽齒輪17，該太陽齒 輪17嚅合有並驅動複數之行星齒輪13，該複數之行星齒 輪13則嚅合於一内環齒輪12内，該内環齒輪12設有一齒 輪軸18，該齒輪軸18上之一端設有外齒181，必須說明的 是，為簡化圖面，圖一至圖三僅顯示一組行星齒輪13，該 複數之行星齒輪13係設置於一固定托板15上，該固定托 板15則設置於一前齒輪箱殼16内，請同時參閱圖四及圖 五，該行星齒輪13係由一外環齒輪131、一軸設於外環齒 輪内之靜壓軸承132、一軸設於靜壓軸承132内及托板15 10 1284182 * 一 / 上之固定銷133所構成，該固定銷133與靜壓軸承132之 • 間具有一間隙dl以形成油道31，該靜壓軸承132具有徑 _ 向貫通靜壓軸承132本體之油道32，該軸承132外侧壁具 有凹槽1321連通油道32，使靜壓軸承132外側壁與外環 齒輪131内側壁形成一間隙d2，該凹槽1321可具有儲油 作用，其次，該托板15係為一夾層架構，其内具成複數之 油道151，該油道151之一端連接外部油管3，另一端則與 該行星齒輪13之油道31形成通路，如圖四所示，該複數 ⑩ 之油道151具有朝向靜壓軸承132之通孔152，以及朝向 行星齒輪13間之通孔153 ;藉由上述之隱藏式油道設計， 可將潤滑油自外部油管3導入托板15之油道151，部分潤 滑油經由通孔152進入油道31，可於固定銷133與靜壓軸 承132之間隙dl形成油膜提供潤滑作用，潤滑油再流經油 道32至靜壓軸承132與外環齒輪131間之凹槽1321，藉 由凹槽1321具有之儲油功能，提供靜壓軸承132與外環齒 輪131轉動時之潤滑作用，而部分潤滑油經由通孔153喷 φ 出於行星齒輪13間，其較佳之喷射角度0約為28°，可提 供行星齒輪13與太陽齒17以及内環齒輪12嚅合之齒間潤 滑。 該第二級齒輪組20，其具有一後齒輪箱外殼26與前 述第一級齒輪組10之前齒輪箱殼16以螺栓相螺合，該第 二級齒輪組20具有一用以輸出低速高扭力軸功馬力之馬 力輸出軸21，該馬力輸出軸21朝向第一級齒輪組10之一 _ 端設有一可隨馬力輸出轴21轉動之法蘭25，於該法蘭25 朝向第一級齒輪組10之面上設有複數之行星齒輪23，該 1284182 > ' 複數之行星齒輪23係同時與前述第一級齒輪組10之齒輪 • 軸18上之外齒181相嚅合，以及固設於前齒輪箱殼16之 ^ 一内環齒14，該行星齒輪23係由一外齒輪231、一軸設於 外齒輪内之靜壓軸承232、一軸設於靜壓軸承232内及法 蘭25上之固定銷233所構成，其構造及功能與前述第一級 齒輪組10所採用之行星齒輪13相同，故在此不再予以贅 述；必須說明的是有關該第二級齒輪組20之隱藏式油道設 計，該馬力輸出軸2内設有一軸向凹槽211，軸向凹槽211 φ 連通一徑向貫通馬力輸出軸2之油道43，以及複數之斜向 貫通馬力輸出軸2及法蘭25之通往行星齒輪23之通孔 252，該通孔252貫穿法蘭25後係朝向靜壓軸承232，其 作用與圖四所示之通孔152相同，該通孔252另旁通有通 孔253朝向行星齒輪23間，該通孔252、253所能達到之 功能與圖四所示之通孔152、153相同，在此亦不予以贅 述；由於該馬力輪出軸21係呈轉動狀態，故與外部油管4 之間必須設置一連接件5，該連接件5包括一固定襯環51， φ 該固定襯環51係固設於後齒輪箱外殼26所具有之一固定 結構261下，該固定結構261係供外部油管4穿設，該固 定襯環51具有一内環形油道41用以承接外部油管4提供 之潤滑油通過，於固定襯環51與馬力輸出軸21之間設有 一軸套53，該軸套53係套設於馬力輸出軸21外，其與固 定襯環51之間設有一軸承54，該軸套53具有一對應油孔 42，該油孔42之一端連通固定襯環51之油道41，另一端 " 則連通徑向貫通馬力輸出軸2之油道43，該軸套53、馬力 輸出軸21、轴承54係呈干涉配合，故可一體同步轉動， 1284182 / 而該固定襯環51與軸套53之間具有一間隙d3，使得軸套 \ 53隨馬力輸出軸21同步轉動時不致對固定襯環51形成干 涉；藉由上述之隱藏式油道設計，可將潤滑油自外部油管 4經由油道41、42、43導入軸向凹槽211並儲存於其内， 儲存於軸向凹槽211内之潤滑油再經由通孔252、253通往 該複數之行星齒輪23及喷出於行星齒輪23間，其所能達 到之功效與前述第一級齒輪組10之行星齒輪13之隱藏式 油道設計相同，不再予以贅述。 • 根據上述可知，本發明所採用之高速、高負載靜壓軸 承131、232運轉時之連續潤滑油膜可提供齒輪重量支撐， 且較傳統輥針軸承可提高轉速，節省空間，故對於該靜壓 軸承131、232必須滿足下列要求： 一、 有良好之耐壓及耐疲勞強度以承受極高之負荷，同時 必須具有軟質與低熔點及低彈性模數； 二、 必須能抵抗磨損或外來雜質進入； 三、 抵抗磨損及摩擦係數之大小，因所有的軸承均須在薄 * 膜潤滑的條件下運轉一段時間之故； 四、 抗腐蝕性； 五、 製造成本。 依據靜壓軸承設計規範，軸承間隙與負荷、表面粗度、 軸頸直徑、材質、使用線速度有關，而潤滑油黏滯度、清 ' 淨度、溫度、壓力變化影響亦很大，為滿足上述特性要求， 本發明之靜壓軸承可採用AISI 1045之中碳合金鋼為基材 施以調質處理，其硬度高、成本低且易於製造，再使用喷 13 1284182 使厚度約Q. 5_之錫絲承合金相著於該中碳合 :土材上’再經精車、拋光表面塗層至最終使用尺廿 =錫基合金以86，％錫、2. 7〜3. 5%銅、㈠揭斑盆他金 屬之比例構成為最佳。 W、金^284182 IX. Description of the invention: [Technical field of the invention] The present invention relates to a secondary planetary gear reduction mechanism, in particular to a high-speed low-torque shaft power horsepower inputting an engine power source end into a low-speed high-torque force The output shaft power horsepower speed reduction mechanism, the second stage of the sun tooth directly coupled with the first stage inner ring tooth integral two-stage reduction gear set matching method is lower than the conventional technology, the economic value of the manufacturing cost and the volume can be reduced. Luqi's concealed oil passage design can provide both hydrostatic bearing and inter-tooth lubrication. Furthermore, the planetary gearbox structure is coaxial with the output and the input shaft, which saves the gearbox compared with the traditional parallel shaft configuration. The use of space, and its high-speed, high-load static housing bearing with a special tin-based bearing alloy formula, can provide high wear resistance, pressure resistance, corrosion resistance and fatigue strength of the bearing. [Prior Art] Planetary gears, which are widely used in the mechanical industry, are mainly used for the reduction mechanism. The basic structure can be referred to the US Patent 4,656,891 US Patent Planetary Gear Box With two double eccentrics or the US Patent 4,986,802 US Patent r pianetary gearb〇 The content of xf〇ra Gan = ck" - in general, the use of the planetary gear speed reduction mechanism, ^ this must be recorded in the m field, outside the wheel of the material around the building 1 < and = gear, thereby multi-stage gear The setting can achieve the purpose of deceleration. The common shortcoming of the star gear reduction mechanism is that its five U-series are used in series, which is complex in structure, bulky and takes up space; 't pieces must withstand high speed and high load. Therefore, the lubricity of 1,284,182 can be very demanding, especially for bearing bearing gears, the oil circuit system must be set to provide lubrication, thus complicating the lubricating oil circuit system. SUMMARY OF THE INVENTION In view of the lack of the prior art, the main object of the present invention is to provide a secondary planetary gear that can convert the high-speed low-torque shaft power of the engine power source input into a low-speed, high-torque output shaft power horsepower. The speed reduction mechanism adopts a two-stage reduction gear set matching method which is lower than the traditional technology and has the economic value of the present. A secondary object of the present invention is to provide a two-stage planetary gear reduction mechanism, in which the second-stage sun gear is directly coupled with the first-stage inner ring gear, and the two-stage reduction gear set is combined with a lower manufacturing cost than the conventional technology. The economic value and the volume can be reduced. Another object of the present invention is to provide a secondary planetary gear reduction mechanism in which the concealed oil passage design can simultaneously provide the hydrostatic bearing and the lubrication between the teeth. A further object of the present invention is to provide a two-stage planetary gear reduction mechanism, wherein the planetary gearbox structure has a coaxial output line and an input shaft, and the gearbox of the conventional parallel shaft arrangement saves space. Another object of the present invention It is to propose a two-stage planetary gear reduction mechanism. Its high-speed, high-load hydrostatic bearing has a special tin-based bearing alloy to provide high wear resistance, pressure resistance, corrosion resistance and fatigue resistance. . In order to achieve the above object, the present invention provides a secondary planetary gear reduction: 1284182 I mechanism, a secondary planetary gear reduction mechanism, comprising: ^ a first stage gear set having a horsepower input shaft for inputting high speed and low speed a torque shaft power horsepower, the horsepower input shaft shaft is connected to a sun gear and a plurality of planetary gears, and the plurality of planetary gears are coupled to an inner ring gear, wherein the inner ring gear is provided with a gear shaft, and the gear shaft is One end is provided with external teeth; a second stage gear set has a horsepower output shaft for outputting low speed high torque shaft power horsepower, the horsepower output shaft is provided with a plurality of planetary gears, • the plurality of planetary gear trains and the foregoing The external gears of the gear shaft of the first stage gear set are phased. Preferably, the plurality of planetary gear trains of the first stage gear set are disposed on a fixed pallet, and the plurality of planetary gear trains of the second stage gear set are disposed on a flange connecting the horsepower output shaft (Flange) In the above, the fixed pallet and the horsepower output shaft flange each have a plurality of oil passages, one end of the oil passage leads to the outer oil pipe, and the other end connects the plurality of planetary gears. Preferably, the planetary gear train comprises: - an outer ring gear; a hydrostatic bearing, the shaft is disposed in the outer ring gear, has an oil passage radially extending through the center of the bearing, and is provided with a concave surface on the outer side wall of the hydrostatic bearing The groove communicates with the oil passage; a fixing pin, the shaft is disposed in the hydrostatic bearing and the pallet, and the oil rail between the fixing pin and the hydrostatic bearing, and the oil passage and the radial oil passage of the static bearing Connected; - The oil passage of the pallet communicates with the oil passage between the fixed pin and the hydrostatic bearing, and the radial oil passage of the hydrostatic bearing to form a passage. "1284182 y Preferably, the hydrostatic bearing system is a tin-based alloy. Preferably, the tin-based alloy is mainly composed of 86 to 90% tin, 2. 7 to 3. 5% copper, - 6 to 7. 5% recorded in proportion to other metals. Preferably, the fixing pin and the hydrostatic bearing have a gap which communicates with the oil passage of the pallet; the recess of the outer side wall of the hydrostatic bearing forms a sidewall of the hydrostatic bearing and an inner sidewall of the outer ring gear. The static bearing has at least one oil passage that radially penetrates the hydrostatic bearing body, and one end of the oil passage is in communication with a groove provided on the outer side wall of the static pressure bearing. Preferably, the first stage gear set and the second stage gear set plate each have a plurality of oil passages, the plurality of oil passages having a plurality of through holes, a part of the through holes facing the static pressure bearing, and a part of the through holes facing the planet Gear room. Preferably, an axially closed groove is formed in the horsepower output shaft of the second stage gear set to form an oil storage chamber, and the oil storage chamber is connected to a plurality of oil passages of the radial through-horse output shaft, and a plurality of oblique directions The through-hole of the horsepower output shaft flange is connected to the through hole of the planetary gear, and a connecting piece is arranged between the oil storage chamber and the outer oil pipe of the horsepower output shaft, so that the connecting member comprises: a bushing, which is fixed to the gear box case In the inner hole, the gear box shell is provided for the outer oil pipe to be penetrated, the inner ring has an inner annular oil passage for receiving the lubricating oil provided by the outer oil pipe, and a bearing is arranged between the fixed ring ring and the horsepower output shaft; a bushing sleeve is disposed outside the horsepower output shaft, and is disposed between the bushing ring and the bushing. The bushing has a bearing, the bushing has a through hole, and one end of the oil hole can communicate with the annular oil passage in the bushing. The other end is fixed to the connecting radial through horse: 1284182 - „ *- force output shaft oil passage, • the bushing, the horsepower output shaft, the bearing inner ring system is interference fit, can be synchronously rotated, and the fixed lining There is a gap between the ring and the sleeve Therefore, when the sleeve rotates synchronously with the horsepower output shaft, it does not interfere with the fixed lining ring. In order to enable the reviewing committee to have a better understanding and approval of the structural purpose and function of the present invention, the detailed description of the drawing is as follows. The technical means and efficacy of the present invention for achieving the object will be described below with reference to the accompanying drawings, and the embodiments listed in the following drawings are only for the purpose of explanation, and are to be understood by the reviewing committee, but the technology of the present invention The means is not limited to the illustrated figures. Referring to Figures 1 to 3, the second-stage planetary gear reduction mechanism provided by the present invention is shown in Figure 1 by the first-stage gear set 10 and Figure 2 The first stage gear set 10 has a horsepower input shaft 11 for inputting a high-speed low-torque shaft power horsepower, and the horsepower input shaft 11 is axially disposed and drives a sun gear 17 The sun gear 17 is coupled to and drives a plurality of planetary gears 13 . The plurality of planetary gears 13 are coupled to an inner ring gear 12 , and the inner ring gear 12 is provided with a gear shaft 18 . One end of the gear shaft 18 is provided with external teeth 181. It should be noted that, in order to simplify the drawing, only one set of the planetary gears 13 is shown in FIG. 1 to FIG. 3 , and the plurality of planetary gears 13 are disposed on a fixed pallet 15 . The fixed pallet 15 is disposed in a front gear housing 16 . Please refer to FIG. 4 and FIG. 5 simultaneously. The planetary gear 13 is composed of an outer ring gear 131 and a static pressure bearing 132 disposed in the outer ring gear. A shaft is disposed in the hydrostatic bearing 132 and a fixing pin 133 on the pallet 15 10 1284182 *, and a gap dl is formed between the fixing pin 133 and the hydrostatic bearing 132 to form an oil passage 31. The bearing 132 has a diameter _ toward the oil passage 32 of the body of the hydrostatic bearing 132. The outer side wall of the bearing 132 has a groove 1321 communicating with the oil passage 32, so that the outer side wall of the hydrostatic bearing 132 forms a gap d2 with the inner side wall of the outer ring gear 131. The groove 1321 can have an oil storage function. Secondly, the pallet 15 is a sandwich structure having a plurality of oil passages 151 therein. One end of the oil passage 151 is connected to the outer oil pipe 3, and the other end is connected to the planetary gear. The oil passage 31 of 13 forms a passage, as shown in FIG. 4, the plural number 10 The oil passage 151 has a through hole 152 facing the hydrostatic bearing 132 and a through hole 153 facing the planetary gear 13; the lubricating oil can be introduced from the outer oil pipe 3 into the oil passage of the pallet 15 by the concealed oil passage design described above. 151, part of the lubricating oil enters the oil passage 31 via the through hole 152, and the oil film is formed in the gap dl between the fixing pin 133 and the static pressure bearing 132 to provide lubrication, and the lubricating oil flows through the oil passage 32 to the static pressure bearing 132 and the outer ring gear. The groove 1321 of the 131 is provided with the oil storage function of the groove 1321 to provide lubrication when the static pressure bearing 132 and the outer ring gear 131 rotate, and part of the lubricating oil is sprayed through the through hole 153 for the planetary gear 13 Preferably, the injection angle 0 is about 28°, and the inter-tooth lubrication of the planetary gear 13 and the sun gear 17 and the inner ring gear 12 can be provided. The second stage gear set 20 has a rear gearbox housing 26 screwed to the gearbox housing 16 of the first stage gear set 10, and the second stage gear set 20 has a low speed and high torque output. An output shaft 21 of the shaft power horsepower, the horsepower output shaft 21 is disposed at one end of the first stage gear set 10 with a flange 25 rotatable with the horsepower output shaft 21, and the flange 25 faces the first stage gear set A plurality of planet gears 23 are provided on the face 10, and the 1284182 > 'plural planetary gears 23 are simultaneously coupled with the external gears 181 of the gears of the first stage gear set 10 and the shaft 18, and are fixed to An inner ring gear 14 of the front gear case 16 , the planetary gear 23 is composed of an outer gear 231 , a static bearing 232 disposed in the outer gear, and a shaft disposed in the hydrostatic bearing 232 and the flange 25 . The fixing pin 233 is configured and has the same structure and function as the planetary gear 13 used in the first stage gear set 10, and therefore will not be described again herein; the hidden oil related to the second stage gear set 20 must be described. In the circuit design, the horsepower output shaft 2 is provided with an axial groove 211, the shaft The groove 211 φ is connected to an oil passage 43 that radially penetrates the horsepower output shaft 2, and a plurality of through holes 252 that extend obliquely through the horsepower output shaft 2 and the flange 25 to the planetary gear 23, the through hole 252 penetrating the flange 25 is oriented toward the hydrostatic bearing 232, and its function is the same as the through hole 152 shown in FIG. 4, and the through hole 252 is further bypassed with the through hole 253 facing the planetary gear 23, and the through hole 252, 253 can achieve the function. The same as the through holes 152, 153 shown in FIG. 4, and will not be described here; since the horsepower wheel shaft 21 is in a rotating state, a connecting member 5 must be disposed between the outer oil pipe 4 and the connecting member 5; The fixing bushing 51 is fixed to the rear gearbox housing 26 and has a fixing structure 261. The fixing structure 261 is provided for the outer oil pipe 4, and the fixing bushing 51 has a fixing bushing 51. The inner annular oil passage 41 is configured to receive the lubricating oil provided by the outer oil pipe 4, and a bushing 53 is disposed between the fixed bushing 51 and the horsepower output shaft 21, and the bushing 53 is sleeved outside the horsepower output shaft 21, A bearing 54 is disposed between the fixed bushing 51 and the corresponding bushing 42 has a corresponding oil hole 42. One end of the oil hole 42 communicates with the oil passage 41 of the fixed lining ring 51, and the other end is connected to the oil passage 43 that penetrates the horsepower output shaft 2 in a radial direction. The sleeve 53 and the horsepower output shaft 21 and the bearing 54 are in an interference fit. Therefore, the rotation can be synchronously integrated, 1284182 / and the gap between the fixed collar 51 and the sleeve 53 has a gap d3, so that the sleeve \ 53 does not interfere with the fixed collar 51 when the horsepower output shaft 21 rotates synchronously; The concealed oil passage design can introduce lubricating oil from the external oil pipe 4 into the axial groove 211 via the oil passages 41, 42, 43 and store therein, and the lubricating oil stored in the axial groove 211 passes through the through hole. 252, 253 leads to the complex planetary gear 23 and is sprayed between the planetary gears 23. The achievable effect is the same as the hidden oil passage design of the planetary gear 13 of the first stage gear set 10, and will not be described again. . • According to the above, the continuous lubricating oil film of the high-speed, high-load hydrostatic bearing 131, 232 used in the present invention can provide gear weight support, and can increase the rotational speed and save space compared with the conventional roller bearing, so the static pressure is Bearings 131 and 232 must meet the following requirements: 1. Have good pressure and fatigue strength to withstand extremely high loads, and must have soft and low melting point and low modulus of elasticity; 2. Must be resistant to wear or foreign matter. Third, the resistance to wear and the coefficient of friction, because all bearings must be operated under the conditions of thin * film lubrication for a period of time; Fourth, corrosion resistance; 5, manufacturing costs. According to the design specifications of the hydrostatic bearing, the bearing clearance is related to the load, the surface roughness, the journal diameter, the material, and the line speed. However, the viscosity of the lubricating oil, the clearness, the temperature, and the pressure change are also greatly affected. The above-mentioned characteristics require that the hydrostatic bearing of the present invention can be subjected to quenching and tempering treatment using a carbon alloy steel of AISI 1045 as a base material, which has high hardness, low cost and is easy to manufacture, and then uses a spray 13 1328422 to have a thickness of about Q. 5_ The tin-bearing alloy is affixed to the medium carbonaceous material: on the soil material, and then refined, and the surface coating is applied to the final use of the ruler = tin-based alloy with 86,% tin, 2. 7~3. 5% copper (1) The proportion of the potted metal is the best. W, gold
々經實驗，本發日聽驗5贿浦發電额減速齒輪 才二寸了由3〇〇〇〇rpm減速至1800rpm，扭矩可由318N · m =至5’304Ν·ιη’證明本發明確可達實際功效，综诚m 本發明具有以下特點： 級齒輪組ίο之具有外齒181之齒輪軸18可作為 第二級齒輪組2G之太陽齒’無需#由扣件、聯轴哭等 傳輸動力，較傳統方式具較少零件、較易組裝之優^， 可降低製造成本，具市場競爭力。 ” 一、^馬力輪出、入軸為同軸、線’較傳統平行轴配置方 郎省使用空間。After the experiment, the date of the hearing of the 5 bribe power generation reduction gear is only two inches from 3 rpm to 1800 rpm, the torque can be 318N · m = to 5 '304 Ν · ιη ' prove that the invention is indeed reachable Actual effect, comprehensively m The invention has the following characteristics: The gear wheel set 18 with the external teeth 181 can be used as the sun gear of the second stage gear set 2G, without the need to transmit power by fasteners, couplings, etc. Compared with the traditional method, it has fewer parts and is easier to assemble. It can reduce manufacturing costs and is competitive in the market. 1. The horsepower wheel and the shaft are coaxial and the line is equipped with space than the traditional parallel axis.
其第-級齒輪組1G之托架15固定，而内環齒輪12為 可動，與傳統設置方式相反，故可提古第一 P 四 ^刀攤部份磨耗及負載，使齒輪使用壽命較為平均。 2星齒輪13、23與平行轴設置方式之小齒輪相較， ^有較低節線速度，可提升轴承、齒輪等機件之壽命 及可靠度。 五、 fe臧W道設計，切㈣可提供_件及靜壓轴承 於運動中可靠有效之潤滑，因此可簡化油路系統，並 可減少外部油管之使用，解決空間不足之問題。 六、 隱藏式油道設計同時可提供_件及靜壓軸承潤滑，The bracket 15 of the first-stage gear set 1G is fixed, and the inner ring gear 12 is movable, which is opposite to the conventional setting method, so that the wear and load of the first P-four-knife booth can be improved, so that the gear life is relatively average. . The 2 star gears 13 and 23 are compared with the pinion gears of the parallel shaft setting mode, and have a lower pitch line speed, which can improve the life and reliability of bearings, gears and the like. 5, fe臧W road design, cut (4) can provide _ pieces and static pressure bearings in the movement of reliable and effective lubrication, so it can simplify the oil system, and can reduce the use of external tubing to solve the problem of insufficient space. Sixth, concealed oil passage design can provide _ pieces and hydrostatic bearing lubrication.
14 1284182 故可與渦輪引擎採用相同之潤滑油，例如VG-32，可 降低成本。 七、 靜壓軸承132、232表面被覆油膜之設計可滿足高速運 轉之高耐磨性及高負載所需，避免齒面金屬嚅合時產 生高溫熔著破壞，且較傳統輥針軸承可運轉於更高之 速度。 八、 採用特殊配方製作之錫基合金靜壓軸承，具有良好特 性，可承受高速、高負載運轉。 , 惟以上所述者，僅為本發明之最佳實施例而已，當不 能以之限定本發明所實施之範圍。即大凡依本發明申請專 利範圍所作之均等變化與修飾，皆應仍屬於本發明專利涵 蓋之範圍内，謹請貴審查委員明鑑，並祈惠准，是所至 禱。 【圖式簡單說明】 圖一係本發明之第一級齒輪組之剖面示意圖。 > 圖二係本發明之第二級齒輪組之剖面示意圖。 圖三係本發明之第一級齒輪組與第二級齒輪組組合之剖面 示意圖。 圖四係本發明之第一級齒輪組之隱藏式潤滑油道之示意 圖。 圖五係本發明之行星齒輪結構之分解立體圖。 【主要元件符號說明】 15 1284182 1 0 -第一級齒輪組 11 -馬力輸入軸 12 -内環齒輪 13-行星齒輪 131- 外齒輪 132- 靜壓軸承 1321-凹槽 13 3 -固定銷 14 -内齒環 15- 固定托板 151-油道 152'153-通孔 16- 前齒輪箱殼 17- 太陽齒輪 18 _齒輪轴 181-外齒 2 0 -第二級齒輪組 21 -馬力輸出軸 211-軸向凹槽 23-行星齒輪 231- 外齒輪 232- 靜壓軸承 233- 固定銷 1284182 25- 法蘭（Flange) _ 252、253-通孔 26- 後齒輪箱外殼 2 61 -固定結構 3、4-外部油管 3卜32、4卜42、43-油道 5-連接件 p 51-固定襯環 52、54-軸承 53-軸套 dl、d2、d3-間隙 θ -喷射角度14 1284182 Therefore, the same lubricant as the turbine engine, such as VG-32, can be used to reduce costs. 7. The surface of the hydrostatic bearing 132, 232 is coated with oil film to meet the high wear resistance and high load required for high-speed operation. It avoids the high temperature melting damage when the tooth surface metal is twisted, and can be operated on the traditional roller bearing. Higher speed. 8. Tin-based alloy hydrostatic bearings made of special formula have good characteristics and can withstand high speed and high load operation. However, the above description is only the preferred embodiment of the present invention, and the scope of the present invention is not limited thereto. That is to say, the equivalent changes and modifications made by the applicants in accordance with the scope of the patent application of the present invention should still fall within the scope of the patents of the present invention. I would like to ask your review committee to give a clear explanation and pray for the best. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a schematic cross-sectional view of a first stage gear set of the present invention. > Figure 2 is a schematic cross-sectional view of a second stage gear set of the present invention. Figure 3 is a schematic cross-sectional view showing the combination of the first stage gear set and the second stage gear set of the present invention. Figure 4 is a schematic view of a hidden lubricating oil passage of the first stage gear set of the present invention. Figure 5 is an exploded perspective view of the planetary gear structure of the present invention. [Main component symbol description] 15 1284182 1 0 - First stage gear set 11 - Horsepower input shaft 12 - Inner ring gear 13 - Planetary gear 131 - External gear 132 - Static pressure bearing 1321 - Groove 13 3 - Fixing pin 14 - Inner ring 15 - Fixed plate 151 - Oil passage 152 '153 - Through hole 16 - Front gear housing 17 - Sun gear 18 - Gear shaft 181 - External gear 2 0 - Second stage gear set 21 - Horsepower output shaft 211 - axial groove 23 - planetary gear 231 - external gear 232 - hydrostatic bearing 233 - fixing pin 1284182 25 - flange (Flange) _ 252, 253 - through hole 26 - rear gear housing 2 61 - fixed structure 3 4-External tubing 3 b 32, 4 b 42, 43 - oil passage 5 - connecting piece p 51 - fixed collar 52, 54 - bearing 53 - bushing dl, d2, d3 - gap θ - spray angle