1296675 (1) 九、發明說明 【發明所屬之技術領域】 本發明是涉及一種往復式泵，尤其是涉及往復式泵裝 置的驅動部和減速部的構造。 【先前技術】 往復式泵裝置爲人所熟知的有習知種種的型式，在曰 本實用新型發明登錄第2545985號公報中記載了一種用於 背負式動力噴霧機等的往復式泵裝置。如第1圖所示，爲 了實現小型化，該往復.式泵裝置一體具有，用於使活塞在 壓缸往復運動的並且由曲柄軸100以及連桿102構成的驅 動部104、和使引擎（未圖示）的動力減速並傳送給該驅 動部104的減速部106。 驅動部104和減速部106雖被收容在外殼內，外殼由 如下部分構成：用於將支撐曲柄軸100的軸承108a、108b _ 中一個的l〇8a固定的軸承外殼110 ;收容曲柄軸100的偏 心凸輪1 1 2的曲柄軸箱1 1 4 ;收容設置在曲柄軸1 00上的 大徑齒輪116以及與該齒輪116咬合並降低旋轉速度進行 傳動的小齒輪（小徑齒輪）1 18的齒輪箱120 ;將支撐曲 柄軸100的另一軸承108b，和支撐該安裝有小齒輪118的 輸入軸122的軸承124a、124b中的一個的124b固定，並 且包圍形成將引擎輸出軸與輸入軸122連接的離合器一部 分的缸筒126的離合器外殼128所構成。此外，支撐輸入 軸122的另一個軸承124a固定在齒輪箱120中。 -4- (2) 1296675 上述現有技術的往復式泵裝置串聯設置有2連的泵本 體，工作能力較高。但是，在這種往復式泵裝置中，由於 曲柄軸的軸承間距較長，因此，一般認爲有可能在曲柄軸 上産生較大的彎曲應力。 因此，本發明的目的在於提供一種能夠降低曲柄軸上 産生的彎曲應力的往復式泵裝置。 【發明內容】 b 爲了實現上述目的，本發明提供一種往復式泵裝置， 該裝置包括：驅動部，具有用於驅動往復式泵的活塞的曲 柄軸；減速部，與該驅動部鄰接設置，具有安裝在曲柄軸 上的大齒輪，以及與大齒輪咬合並安裝在輸入動力的輸入 軸上的小齒輪，其特徵爲：將支撐輸入軸，並可使其旋轉 的第一軸承以及第二軸承集中設置在與驅動部相對的一側 ，以懸臂狀支撐輸入軸。 在這種結構中，可以使小齒輪靠近驅動部一側，從而 _ ，也可以使大齒輪向利用連桿與活塞連結的曲柄軸的偏心 凸輪接近。因此，可縮短曲柄軸的全長，降低曲柄軸上産 生的彎曲應力。 在本發明的往復式泵裝置中，適於採用如下設置：第 一軸承支撐與輸入軸的軸線垂直方向的負載，並支撐遠離 沿輸入軸軸線方向的小齒輪方向的負載；第二軸承支撐與 輸入軸的軸線垂直方向的負載，並支撐朝向沿輸入軸的軸 線方向的小齒輪方向的負載；而且’減速部的外殼中，在 -5- (3) 1296675 收容第一軸承以及第二軸承的空間的內周面上設置凸部， 在該凸部與小齒輪之間夾有第一*軸承，同時’在凸部與女 裝於輸入軸上的止動手段之間夾有第二軸承。可以預先在 外殼上組裝第一軸承及第二軸承，從而提高裝配效率。 如上上述，根據本發明，利用將支撐輸入軸的兩個軸 承集中安裝於減速部的外側，並以懸臂狀支撐輸入軸，使 小齒輪靠近驅動部一側，因而可將大齒輪的位置配置在偏 心凸輪的附近。從而，可縮短支撐曲柄軸兩端的軸承之間 b 的距離，減少施加在曲柄軸上的彎曲應力。這也減少了對 軸承的負擔，使往復式泵裝置的可靠性得以提高。 除了可以縮短曲柄軸的長度之外，通過將支撐輸入軸 的軸承集中設於一側的方法，可省去相當於現有技術中的 齒輪箱構件。因此，零件數量減少，組裝作業變得容易。 組裝時的累積公差變小，這樣不僅有助於提高大齒輪與小 齒輪的咬合精度，也有助於提高軸承的耐久性。1296675 (1) Description of the Invention [Technical Field] The present invention relates to a reciprocating pump, and more particularly to a configuration of a driving portion and a speed reducing portion of a reciprocating pump device. [Prior Art] A reciprocating pump device is known in the art, and a reciprocating pump device for a knapsack power sprayer or the like is described in Japanese Laid-Open Patent Publication No. 2545985. As shown in Fig. 1, in order to achieve miniaturization, the reciprocating pump device integrally has a driving portion 104 for reciprocating a piston in a cylinder and constituted by a crank shaft 100 and a connecting rod 102, and an engine ( The power (not shown) is decelerated and transmitted to the speed reducing portion 106 of the drive unit 104. The drive unit 104 and the speed reduction unit 106 are housed in the casing, and the outer casing is constituted by a bearing housing 110 for fixing one of the bearings 108a and 108b_ supporting the crankshaft 100, and a crankshaft 100 for housing the crankshaft 100. The crankcase 1 1 4 of the eccentric cam 1 1 2; the large-diameter gear 116 housed on the crankshaft 100 and the gear of the pinion (small-diameter gear) 1 18 that is engaged with the gear 116 to reduce the rotational speed for transmission a case 120; fixing another bearing 108b supporting the crankshaft 100, and 124b supporting one of the bearings 124a, 124b of the input shaft 122 to which the pinion 118 is mounted, and surrounding forming to connect the engine output shaft with the input shaft 122 The clutch is formed by a clutch housing 128 of a portion of the cylinder 126. Further, another bearing 124a supporting the input shaft 122 is fixed in the gear case 120. -4- (2) 1296675 The above-described prior art reciprocating pump device is provided with two pump bodies in series, and has a high working capacity. However, in such a reciprocating pump device, since the bearing pitch of the crankshaft is long, it is considered that it is possible to generate a large bending stress on the crankshaft. Accordingly, it is an object of the present invention to provide a reciprocating pump apparatus capable of reducing bending stress generated on a crankshaft. SUMMARY OF THE INVENTION In order to achieve the above object, the present invention provides a reciprocating pump device including: a driving portion having a crank shaft for driving a piston of a reciprocating pump; and a speed reducing portion disposed adjacent to the driving portion, having a large gear mounted on the crankshaft, and a pinion that is coupled to the large gear and mounted on the input shaft of the input power, characterized in that: the first bearing and the second bearing that support the input shaft and can rotate The input shaft is supported in a cantilever manner on the side opposite to the driving portion. In this configuration, the pinion gear can be brought closer to the side of the driving portion, so that the large gear can be brought close to the eccentric cam of the crankshaft to which the connecting rod and the piston are coupled. Therefore, the overall length of the crankshaft can be shortened, and the bending stress generated on the crankshaft can be reduced. In the reciprocating pump device of the present invention, it is suitable to adopt an arrangement in which the first bearing supports a load perpendicular to the axis of the input shaft and supports a load away from the pinion direction in the direction of the input shaft axis; the second bearing supports and Input the load in the vertical direction of the axis of the shaft and support the load in the direction of the pinion gear in the direction of the axis of the input shaft; and in the outer casing of the 'deceleration portion, the first bearing and the second bearing are accommodated at -5-(3) 1296675 A convex portion is disposed on the inner peripheral surface of the space, and a first * bearing is interposed between the convex portion and the pinion gear, and a second bearing is sandwiched between the convex portion and the stopper means of the wearer on the input shaft. The first bearing and the second bearing can be assembled in advance on the outer casing to improve assembly efficiency. As described above, according to the present invention, the two bearings supporting the input shaft are collectively attached to the outer side of the speed reducing portion, and the input shaft is supported in a cantilever manner so that the pinion gear is close to the driving portion side, so that the position of the large gear can be arranged at Near the eccentric cam. Thereby, the distance between the bearings b supporting the ends of the crankshaft can be shortened, and the bending stress applied to the crankshaft can be reduced. This also reduces the burden on the bearings and increases the reliability of the reciprocating pump unit. In addition to shortening the length of the crankshaft, by concentrating the bearings supporting the input shaft on one side, the gearbox member equivalent to the prior art can be omitted. Therefore, the number of parts is reduced, and assembly work becomes easy. The cumulative tolerance during assembly is reduced, which not only helps to improve the bite accuracy of the large gear and the pinion, but also contributes to the durability of the bearing.
I 【實施方式】 以下，對本發明的往復式泵裝置的較佳實施型態詳細 說明如下。 第2圖是本發明的往復式泵裝置的部分剖面圖，第3 圖是沿著第2圖中的III-III線的部分剖面圖。圖示的往復 式泵裝置1 〇，在兩個往復式泵1 2在相向的狀態下設置成 一列。各個往復式泵12包括：壓缸14、在壓缸14內往復 運動的活塞16、排出閥18、以及吸水閥20;其中，通過 -6- (4) 1296675 活塞1 6的往復運動，液體從吸水口 22經過流路24，並流 經流路26從排出口 28排出。由於各個往復式泵12交互 運作，所以將液體不斷地供給至流路26，使得液體可高效 穩定地從排出口 2 8排出。 用於驅動活塞16的驅動部30位於兩個往復式泵12 之間，基本結構包括，曲柄軸3 2以及安裝在曲柄軸3 2的 偏心凸輪3 4上並與各個往復式泵1 2的活塞1 6連接的連 桿3 6。爲了減少磨損，在曲柄軸3 2的偏心凸輪3 4與連桿 I 3 6之間設置軸承3 8。曲柄軸3 2 —旦旋轉，則通過軸承3 8 .和連桿3 6將旋轉運動轉換爲往復運動，使活塞1 6往復運 動。將曲柄軸3 2、連桿3 6以及軸承3 8收容在第一外殼 40內。 此外，從適當的外部驅動源，例如引擎（未圖示）向 曲柄軸32提供動力，由於引擎輸出軸的旋轉速度很高’ 因此，將減速至適當轉速並傳遞給曲柄軸32的減速部42 ，與驅動部30鄰接設置成一個整體。從而，使往復式泵 > 裝置10形成一個小型整體，適用於背負式動力噴霧機等 〇 減速部42包括：安裝在曲柄軸32上的大齒輪44、與 該大齒輪44咬合的小齒輪46。小齒輪46安裝在輸入引擎 動力的輸入軸48上，在該輸入軸48的外側端部，安裝有 稱爲缸筒（止動手段）50的離合器（clutch)機構的一部 分。離合器機構，可斷接地將引擎輸出軸的旋轉驅動力傳 遞給輸入軸48。由於減速部42採用這種構造，因此’通 1296675 (5) 過引擎將高速的旋轉傳遞給輸入軸48時，該旋轉從齒數 較少的小齒輪46傳遞給齒數較多的大齒輪44，並減速至 預期的旋轉速度。 減速部42的大齒輪44以及小齒輪46收容於第一外 殻40以及與其相結合的第二外殼52之間的空間，此外， 輸入軸48以及缸筒50收容在第二外殼52內。 利用軸承5 4、5 6支撐曲柄軸3 2的兩端部，並可使其 旋轉。其中一個軸承54固定於第一外殼40，另一個軸承 t 56固定於第二外殼52。 另一方面，在輸入軸48的驅動部3 0 —側的端部未設 置軸承，而是安裝有小齒輪46。將用於支撐輸入軸48的 第一軸承58以及第二軸承60設置在從小齒輪46朝向與 驅動部3 0相反一側延伸的部分上，並以懸臂狀支撐輸入 軸48。 第一軸承58以及第二軸承60收容在形成於第二外殼 > 52中的圓筒形的空間62內。在該空間62的內周面上形成 有環形的凸部64，以夾持該凸部64的方式設置第一軸承 5 8以及第二軸承6 0。而且，利用小齒輪4 6和缸筒5 0夾 持該兩個軸承58、60，以使其不會從空間62中脫落。 在本實施型態中，第一軸承5 8以及第二軸承6 0，均 爲滾珠軸承，可支撐與輸入軸4 8軸線垂直方向的負載（ 徑向負載），以及沿輸入軸4 8的軸線方向的負載（軸向 負載），即所謂的徑向/軸向軸承。當在輸入軸48上作用 有朝向與驅動部3 0相反一側的負載，即朝著外側的軸向 -8 - (6) 1296675 負載時，對於第一軸承58 ’確定其方向，並夾持在凸部 64和小齒輪46之間’以使其能夠支撐該負載。另一方面 ，當在輸入軸48上作用有朝向驅動部30 —側的負載’即 朝向小齒輪4 6的軸向負載時’使第二軸承6 0與第一軸承 5 8相向設置，並夾持在凸部64與缸筒5 0之間，以使其能 夠支撐該負載。通過上述結構，對於沿著其軸線的兩個方 向的軸向負載及徑方向的徑向負載，可確實地支撐輸入軸 48 ° > 並且，爲了不妨礙輸入軸48的旋轉，凸部64僅與第 一軸承58以及第二軸承60的外圈接觸，小齒輪46僅與 第一軸承58的內圈接觸，缸筒50僅與第二軸承60的內 圈接觸。 在上述的結構中，由於將第一軸承5 8以及第二軸承 60集中設置在輸入軸48的一側，因此無須使輸入軸48的 驅動部30 —側的端部從小齒輪46突出。因此，可使小齒 輪46靠近驅動部3 0 —側。從而，可使與小齒輪46咬合 b 的大齒輪44接近偏心凸輪34，而且還可縮短曲柄軸32的 全長。通過將第2圖與現有技術結構的第1圖進行比較， 可以很容易明白。曲柄軸3 2的兩端雖是由軸承5 4、5 6支 撐，但是，由於軸承54、56之間的距離也變短，因此， 可以減少作用於曲柄軸3 2的徑向力所産生的彎曲應力。 當然’也會減少作用於軸承5 4、5 6的反作用力。因此， 提高了曲柄軸32以及軸承54、56的耐久性，及往復式泵 裝置10的可靠性，同時也延長了其使用壽命。 (7) 1296675 此外，在上述結構中9將支撑輸入軸4 8的第一軸承 58以及第二軸承60集中設置在一側，並由小齒輪46與缸 筒50夾持，因此，可在第二外殼52上預先組裝小齒輪46 、第一軸承58以及第二軸承60、輸入軸48以及缸筒50 。因此，在本實施型態中，由第2圖可知，可以只用兩個 外殼40、52來收容驅動部30與減速部42。在現有技術中 ，如第1圖所示，由於在輸入軸122的兩端安裝有軸承 124a、124b，因此，必須另外準備用於固定作爲驅動部 > 104 —側的軸承124a的外殼（齒輪箱）120，顯然，組裝 工藝繁瑣，而且産生因組裝零件數衆多導致總公差變大的 問題，而在本實施例中則沒有這樣的問題。因此，也容易 提高大齒輪44與小齒輪46之間的精度，其結果，有助於 提高大齒輪44及小齒輪46、軸承54、56、58、60的耐久 性。除此之外，還有助於提高往復式泵裝置1 〇的可靠性 等。 _ 以上，對本發明的較佳實施型態進行了詳細說明，當 然本發明也並非局限於上述實施型態。例如，在上述實施 型態中，雖是利用缸筒5 0固定第一軸承5 8以及第二軸承 60，但是，也可以在輸入軸48上安裝軸承固定專用的環 等止動手段。此外，本發明對於只有一個、或者有三個以 上往復式泵的裝置也同樣適用。 【圖式簡單說明】 通過基於附圖所進行的以下詳細說明以及申請專利範 -10- (8) 1296675 圍，可以瞭解本發明的上述特徵和效果以及其他特徵和效 果。添附圖面中， 第1圖是先前技術的往復式泵裝置的部分剖面圖。 第2圖是本發明的往復式泵裝置的一實施型態的部分 剖面圖。 第3圖是沿第2圖的III-III線的部分剖面圖。 【主要元件符號說明】 _ 10:往復式泵裝置 1 2 :往復式泵 1 4 :活塞 1 6 ·活塞 20 :吸水閥 28 :排出口 3 〇 :驅動部 32 :曲柄軸 3 4 :偏心凸輪 36 :連桿 3 8 :軸承 40 :外殻 4 2 :減速部 4 4 :大齒輪 46 :小齒輪 48 :輸入軸 -11 - (9) 1296675 5 Ο :缸筒 52 :第二外殼 5 4 :軸承 5 6 :軸承 5 8 :第一軸承 6 0 :第二軸承 62 :空間 64 :凸部 100 :曲柄軸 102 :連桿 1 0 4 :驅動部 106 :減速部 108a、 108b ：軸承 1 1 0 ::軸承箱[Embodiment] Hereinafter, preferred embodiments of the reciprocating pump device of the present invention will be described in detail below. Fig. 2 is a partial cross-sectional view showing a reciprocating pump device of the present invention, and Fig. 3 is a partial cross-sectional view taken along line III-III in Fig. 2; The reciprocating pump unit 1 shown in the figure is arranged in a row in the state in which the two reciprocating pumps 12 are opposed to each other. Each of the reciprocating pumps 12 includes a cylinder 14, a piston 16 that reciprocates within the cylinder 14, a discharge valve 18, and a suction valve 20; wherein, by the reciprocation of the -6-(4) 1296675 piston 16 The water suction port 22 passes through the flow path 24 and flows through the flow path 26 to be discharged from the discharge port 28. Since the respective reciprocating pumps 12 operate alternately, the liquid is continuously supplied to the flow path 26, so that the liquid can be efficiently and stably discharged from the discharge port 28. The driving portion 30 for driving the piston 16 is located between the two reciprocating pumps 12, and the basic structure includes a crank shaft 32 and a piston mounted on the eccentric cam 34 of the crank shaft 32 and with the pistons of the respective reciprocating pumps 12. 1 6 connected links 3 6. In order to reduce wear, a bearing 38 is provided between the eccentric cam 34 of the crankshaft 32 and the link I 36. When the crank shaft 3 2 is rotated, the rotary motion is converted into a reciprocating motion by the bearing 38 and the link 36, and the piston 16 is reciprocated. The crankshaft 3, the connecting rod 36, and the bearing 38 are housed in the first outer casing 40. In addition, power is supplied to the crankshaft 32 from a suitable external drive source, such as an engine (not shown), since the rotational speed of the engine output shaft is high 'Thus, the speed is reduced to the appropriate speed and transmitted to the deceleration portion 42 of the crankshaft 32. It is disposed integrally with the drive unit 30. Accordingly, the reciprocating pump > device 10 is formed into a small unit, and the slewing portion 42 for use in a knapsack power sprayer or the like includes a large gear 44 mounted on the crank shaft 32, and a pinion 46 engaged with the large gear 44. . The pinion 46 is mounted on an input shaft 48 for inputting engine power, and a portion of a clutch mechanism called a cylinder (stop means) 50 is attached to the outer end of the input shaft 48. The clutch mechanism can be grounded to transmit the rotational driving force of the engine output shaft to the input shaft 48. Since the speed reducing portion 42 adopts such a configuration, when the through-wheel 1296965 (5) transmits the high-speed rotation to the input shaft 48 through the engine, the rotation is transmitted from the pinion 46 having a small number of teeth to the large gear 44 having a large number of teeth, and Slow down to the desired rotation speed. The large gear 44 and the pinion gear 46 of the speed reducing portion 42 are accommodated in a space between the first outer casing 40 and the second outer casing 52 coupled thereto, and the input shaft 48 and the cylinder 50 are housed in the second outer casing 52. Both ends of the crankshaft 32 are supported by bearings 5 4, 56 and can be rotated. One of the bearings 54 is fixed to the first outer casing 40, and the other bearing t56 is fixed to the second outer casing 52. On the other hand, a bearing is not provided at the end portion of the input shaft 48 on the side of the drive portion 30, but a pinion 46 is attached. The first bearing 58 and the second bearing 60 for supporting the input shaft 48 are disposed on a portion extending from the pinion gear 46 toward the side opposite to the driving portion 30, and support the input shaft 48 in a cantilever manner. The first bearing 58 and the second bearing 60 are housed in a cylindrical space 62 formed in the second casing > 52. An annular convex portion 64 is formed on the inner peripheral surface of the space 62, and the first bearing 58 and the second bearing 60 are disposed to sandwich the convex portion 64. Moreover, the two bearings 58, 60 are held by the pinion gear 46 and the cylinder 50 so that they do not fall out of the space 62. In the present embodiment, the first bearing 58 and the second bearing 60 are ball bearings that support a load (radial load) perpendicular to the axis of the input shaft 48 and an axis along the input shaft 48. Directional load (axial load), the so-called radial/axial bearing. When a load acting on the opposite side of the input shaft 48 toward the drive portion 30, that is, an axial direction -8 - (6) 1296675 load toward the outer side, the direction is determined for the first bearing 58' and clamped. 'between the projection 64 and the pinion 46 to enable it to support the load. On the other hand, when a load toward the side of the drive portion 30, that is, an axial load toward the pinion 46, acts on the input shaft 48, the second bearing 60 is disposed opposite to the first bearing 58 and clamped. It is held between the convex portion 64 and the cylinder 50 so as to be able to support the load. With the above configuration, the axial load and the radial load in the radial direction along the axial direction can reliably support the input shaft 48° > and, in order not to hinder the rotation of the input shaft 48, the convex portion 64 is only In contact with the outer ring of the first bearing 58 and the second bearing 60, the pinion 46 is in contact only with the inner ring of the first bearing 58, and the cylinder 50 is only in contact with the inner ring of the second bearing 60. In the above configuration, since the first bearing 58 and the second bearing 60 are collectively provided on one side of the input shaft 48, it is not necessary to cause the end portion of the input shaft 48 on the side of the drive portion 30 to protrude from the pinion gear 46. Therefore, the pinion 46 can be brought close to the side of the driving portion 30. Thereby, the large gear 44 that engages with the pinion gear 46 can be brought close to the eccentric cam 34, and the total length of the crank shaft 32 can also be shortened. It can be easily understood by comparing Fig. 2 with Fig. 1 of the prior art structure. Although both ends of the crankshaft 3 2 are supported by the bearings 5 4 and 56 , the distance between the bearings 54 and 56 is also shortened, so that the radial force acting on the crankshaft 32 can be reduced. Bending stress. Of course, the reaction force acting on the bearings 5 4, 5 6 will also be reduced. Therefore, the durability of the crankshaft 32 and the bearings 54, 56 and the reliability of the reciprocating pump device 10 are improved, and the service life thereof is also prolonged. (7) 1296675 Further, in the above configuration, the first bearing 58 and the second bearing 60 supporting the input shaft 48 are collectively disposed on one side, and are held by the pinion 46 and the cylinder 50, and therefore, The pinion 46, the first bearing 58 and the second bearing 60, the input shaft 48, and the cylinder 50 are pre-assembled on the second casing 52. Therefore, in the present embodiment, as is apparent from Fig. 2, the drive unit 30 and the speed reduction portion 42 can be accommodated by only the two outer casings 40, 52. In the prior art, as shown in Fig. 1, since the bearings 124a and 124b are attached to both ends of the input shaft 122, it is necessary to separately prepare a casing (gear) for fixing the bearing 124a as the driving portion > The case 120, obviously, the assembly process is cumbersome, and there is a problem that the total tolerance becomes large due to the large number of assembled parts, and there is no such problem in the present embodiment. Therefore, it is also easy to improve the accuracy between the large gear 44 and the pinion gear 46, and as a result, it contributes to improving the durability of the large gear 44 and the pinion gear 46, and the bearings 54, 56, 58, and 60. In addition to this, it contributes to the improvement of the reliability of the reciprocating pump unit 1 and the like. The preferred embodiments of the present invention have been described in detail above, and the present invention is not limited to the above embodiments. For example, in the above embodiment, the first bearing 58 and the second bearing 60 are fixed by the cylinder 50, but a stopper such as a ring for bearing fixing may be attached to the input shaft 48. Furthermore, the invention is equally applicable to devices having only one or more than three reciprocating pumps. BRIEF DESCRIPTION OF THE DRAWINGS The above features and effects and other features and advantages of the present invention will become apparent from the following detailed description of the invention and the appended claims. In the drawings, FIG. 1 is a partial cross-sectional view of a prior art reciprocating pump device. Fig. 2 is a partial cross-sectional view showing an embodiment of the reciprocating pump device of the present invention. Fig. 3 is a partial cross-sectional view taken along line III-III of Fig. 2; [Main component symbol description] _ 10: Reciprocating pump device 1 2 : Reciprocating pump 1 4 : Piston 1 6 · Piston 20 : Water suction valve 28 : Discharge port 3 〇: Drive portion 32 : Crankshaft 3 4 : Eccentric cam 36 : Connecting rod 3 8 : Bearing 40 : Housing 4 2 : Speed reducing portion 4 4 : Large gear 46 : Pinion 48 : Input shaft -11 - (9) 1296675 5 Ο : Cylinder 52 : Second housing 5 4 : Bearing 5 6 : bearing 5 8 : first bearing 6 0 : second bearing 62 : space 64 : convex portion 100 : crank shaft 102 : connecting rod 1 0 4 : driving portion 106 : speed reducing portion 108a, 108b : bearing 1 1 0 : : bearing housing
1 1 2 :偏心凸輪 1 1 4 :曲柄軸箱 116 :齒輪 1 1 8 :小齒輪 120 :齒輪箱 122 :輸入軸 124a、124b ：軸承1 1 2 : Eccentric cam 1 1 4 : Crank axle box 116 : Gear 1 1 8 : Pinion 120 : Gear box 122 : Input shaft 124a, 124b : Bearing