TWI404872B - Planetary reducer - Google Patents
Planetary reducer Download PDFInfo
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- TWI404872B TWI404872B TW099129695A TW99129695A TWI404872B TW I404872 B TWI404872 B TW I404872B TW 099129695 A TW099129695 A TW 099129695A TW 99129695 A TW99129695 A TW 99129695A TW I404872 B TWI404872 B TW I404872B
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- outer casing
- planetary
- gear
- carrier body
- main bearing
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- 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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
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Abstract
Description
本發明關於一種行星減速機。The invention relates to a planetary reducer.
於專利文獻1所示之行星減速機中，內齒輪與外殼成為分體結構。故，可想到如下：於專利文獻1所示之行星減速機中，即使該外殼於主軸承與對象機械之間具有小於可旋轉地支承輪架體之該主軸承之外圈外徑的內徑部份亦可不使與對象機械之連結形態變更而使行星減速機大容量化。在此，於專利文獻1中，沿軸向壓入頂銷而於外殼固定內齒輪。In the planetary reducer shown in Patent Document 1, the internal gear and the outer casing have a separate structure. Therefore, it is conceivable that in the planetary reducer shown in Patent Document 1, even if the outer casing has an inner diameter smaller than the outer diameter of the outer ring of the main bearing that rotatably supports the carrier body between the main bearing and the target machine In some cases, the planetary reducer can be increased in capacity without changing the connection form with the target machine. Here, in Patent Document 1, the top pin is press-fitted in the axial direction to fix the internal gear to the outer casing.
專利文獻1：WO99/25992號公報Patent Document 1: WO99/25992
然而，於專利文獻1所示之結構中，於輪架體之半徑方向上比壓入頂銷之位置更靠內側配置主軸承。亦即，於專利文獻1所示之行星減速機中，為確保壓入頂銷之空間，必須縮小支承主軸承的外殼部份之內徑。為此，必須使主軸承之直徑縮小，故導致主軸承之容量變小，輸出轉矩或力矩剛性亦變小。又，加大主軸承之直徑時，導致行星減速機本身大型化。However, in the configuration shown in Patent Document 1, the main bearing is disposed on the inner side of the radial direction of the carrier body than the position at which the push pin is pressed. That is, in the planetary reducer shown in Patent Document 1, in order to secure the space for press-fitting the top pin, it is necessary to reduce the inner diameter of the outer casing portion that supports the main bearing. For this reason, the diameter of the main bearing must be reduced, so that the capacity of the main bearing becomes small, and the output torque or torque rigidity also becomes small. Moreover, when the diameter of the main bearing is increased, the planetary reducer itself is enlarged.
故，本發明係為解決前述問題點而完成者，其課題在於，提供一種行星減速機，該行星減速機即使外殼於主軸承與對象機械之間具有小於可旋轉地支承輪架體之該主軸承之外圈外徑的內徑部份亦可不使減速機本身大型化而設置大直徑之主軸承。Therefore, the present invention has been made to solve the above problems, and an object of the invention is to provide a planetary reducer that has a smaller outer diameter between a main bearing and a target machine than a rotatably supported carrier body. The inner diameter portion of the outer diameter of the outer ring of the bearing can also be provided with a large-diameter main bearing without making the reducer itself large.
本發明係藉由如下解決前述課題者：一種行星減速機，具備行星齒輪、該行星齒輪所內接嚙合之內齒輪、與前述行星齒輪之公轉成份或自轉成份同步之輪架體、可旋轉地支承該輪架體之主軸承、於該主軸承與對象機械之間具有小於該主軸承之外圈外徑的內徑部份之外殼，其中，前述外殼於對象機械側和對象機械相反側分體形成，於軸向上比前述內齒輪更靠前述對象機械側配置前述主軸承，於前述對象機械相反側之外殼包含其齒形部而一體形成前述內齒輪，並且前述對象機械側之外殼和前述對象機械相反側之外殼相連結。The present invention is directed to a planetary gear reducer comprising: a planetary gear, an internal gear meshed by the planetary gear, a wheel carrier body synchronized with a revolution component or a rotation component of the planetary gear, and rotatably a main bearing supporting the wheel frame body, and an outer casing having an inner diameter portion smaller than an outer diameter of the outer ring of the main bearing between the main bearing and the target machine, wherein the outer casing is on the opposite side of the mechanical side of the object and the object machine The body is formed such that the main bearing is disposed on the machine side of the target gear in the axial direction, and the outer casing on the opposite side of the target machine includes the toothed portion thereof to integrally form the internal gear, and the outer casing of the object mechanical side and the foregoing The outer casing of the opposite side of the object is connected.
本發明將外殼於對象機械側和對象機械相反側分割成分體，於對象機械相反側之外殼包含齒形部而一體形成內齒輪。故，即使對象機械側之外殼於主軸承與對象機械之間具有小於該主軸承的外圈外徑之內徑部份，亦可將該主軸承(從對象機械相反側)組裝於對象機械側之外殼。According to the present invention, the outer casing is divided into a component body on the opposite side of the object mechanical side and the object machine, and the outer casing on the opposite side of the target machine includes a toothed portion to integrally form the internal gear. Therefore, even if the outer casing of the object mechanical side has an inner diameter portion smaller than the outer diameter of the outer ring of the main bearing between the main bearing and the target machine, the main bearing (from the opposite side of the object machine) can be assembled to the mechanical side of the object. The outer casing.
又，設為將外殼於對象機械側和對象機械相反側分割成分體，於對象機械相反側之外殼包含齒形部而一體形成內齒輪，進而連結對象機械側之外殼和對象機械相反側之外殼的結構，故可不使行星減速機本身大型化而配置大直徑之主軸承。藉此，可加大主軸承之容量，結果可使輸出轉矩或力矩剛性提高。Further, the outer casing is divided into a component body on the opposite side of the target machine side and the target machine, and the outer casing on the opposite side of the target machine includes a toothed portion to integrally form the internal gear, and further connects the outer casing of the target machine side and the outer casing of the object machine side. Since the planetary reducer itself is not large, the large-diameter main bearing can be disposed. Thereby, the capacity of the main bearing can be increased, and as a result, the output torque or the torque rigidity can be improved.
亦即，如先前技術般，將內齒輪與外殼設為分體結構時，或即便將內齒輪與外殼設為一體結構，當將內齒輪與其齒形部設為分體結構時，為將內齒輪或齒形部固定於外殼，亦必須縮小沿軸向與外殼之內齒輪或齒形部鄰接之部份，亦即支承外殼之主軸承的部份之內徑，結果存在或縮小主軸承之直徑，或若不縮小主軸承之直徑，則減速機本身被大型化之問題。That is, as in the prior art, when the internal gear and the outer casing are configured as a separate structure, or even if the internal gear and the outer casing are integrally formed, when the internal gear and the toothed portion thereof are provided as a separate structure, The gear or the toothed portion is fixed to the outer casing, and the portion adjacent to the inner gear or the toothed portion of the outer casing, that is, the inner diameter of the portion of the main bearing of the outer casing, must be reduced, resulting in the presence or reduction of the main bearing. The diameter, or if the diameter of the main bearing is not reduced, the reducer itself is enlarged.
與此相反，本發明藉由具有上述結構，無需縮小沿軸向與外殼之內齒輪鄰接的部份之內徑，故可不使減速機本身大型化而配置大直徑之主軸承。其結果，可加大主軸承之容量並能使輸出轉矩及力矩剛性提高。On the other hand, according to the present invention, since the inner diameter of the portion adjacent to the inner gear of the outer casing in the axial direction is not required to be reduced, the main bearing of the large diameter can be disposed without increasing the size of the reducer itself. As a result, the capacity of the main bearing can be increased and the output torque and torque rigidity can be improved.
根據本發明，可不使行星減速機本身大型化而採用大直徑之主軸承，故可加大主軸承之容量並能使輸出轉矩及力矩剛性提高。According to the present invention, the large-diameter main bearing can be used without increasing the size of the planetary reducer itself, so that the capacity of the main bearing can be increased and the output torque and the torque rigidity can be improved.
以下，參照附圖對本發明之實施形態之一例進行詳細說明。Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings.
圖1係表示本發明之第1實施形態之一例所涉及的行星減速機之主要部份的剖視圖。Fig. 1 is a cross-sectional view showing a main part of a planetary reducer according to an example of the first embodiment of the present invention.
行星減速機100為簡單行星齒輪機構，於外殼136具備有未圖示之太陽齒輪、行星齒輪114、輪架體120、和內齒輪134。再者，外殼136分割成連接於行星減速機100之作為對象機械側之外殼的輸出側外殼138和作為對象機械相反側之外殼的輸入側外殼137。The planetary reducer 100 is a simple planetary gear mechanism, and the outer casing 136 includes a sun gear (not shown), a planetary gear 114, a carrier body 120, and an internal gear 134. Further, the outer casing 136 is divided into an output side outer casing 138 which is connected to the outer casing of the planetary reduction gear 100 as the target mechanical side, and an input side outer casing 137 which is a casing opposite to the object mechanical side.
於太陽齒輪例如設置有斜齒輪(亦可為正齒輪)，與行星齒輪114相嚙合。太陽齒輪例如透過未圖示之圓柱形狀之連接軸連結於未圖示之電動機之電動機軸。The sun gear is provided with, for example, a helical gear (also a spur gear) that meshes with the planetary gear 114. The sun gear is coupled to a motor shaft of a motor (not shown) through, for example, a cylindrical connecting shaft (not shown).
行星齒輪114其多數配置於太陽齒輪之外周，於太陽齒輪周圍自轉的同時公轉。行星齒輪114透過滾針116支承於行星銷118。滾針116以滿滾子狀態配置，於軸向O上分割成2個。故，太陽齒輪與行星齒輪114、行星齒輪114與內齒輪134相嚙合時，可減少滾針116之一端接觸，而且，於無保持器之滿滾子狀態下使用滾針116，故可將較大轉矩傳遞至行星銷118。再者，於2個滾針116之間配置有環形狀之襯墊116A。而且於襯墊116A之內周與行星銷118之外周之間設置有間隙G而成為於間隙G保持潤滑劑(潤滑脂)之結構。故，即使行星齒輪114旋轉亦可將潤滑脂穩定地供給至滾針116。此時，可於襯墊116A之外周與行星齒輪114之內周之間還設置有如保持潤滑脂之間隙。此時，因藉由行星齒輪114之公轉，襯墊116A之中心相對於行星銷118之中心偏心運動，故可將襯墊116A之外周和內周之潤滑脂有效地供給至滾針116。亦即，可使行星齒輪114長壽命化。Most of the planetary gears 114 are disposed on the outer circumference of the sun gear, and revolve around the sun gear while rotating. The planet gears 114 are supported by the planet pins 118 via the needle rollers 116. The needle roller 116 is disposed in a full roller state and is divided into two in the axial direction O. Therefore, when the sun gear meshes with the planetary gear 114, the planetary gear 114 and the internal gear 134, the contact of one end of the needle 116 can be reduced, and the needle 116 can be used in the full roller without the retainer, so The large torque is transmitted to the planet pin 118. Further, a ring-shaped spacer 116A is disposed between the two needle rollers 116. Further, a gap G is provided between the inner circumference of the spacer 116A and the outer circumference of the planetary pin 118, and the lubricant G (grease) is held in the gap G. Therefore, even if the planetary gear 114 rotates, the grease can be stably supplied to the needle roller 116. At this time, a gap such as a grease can be provided between the outer circumference of the spacer 116A and the inner circumference of the planetary gear 114. At this time, since the center of the spacer 116A is eccentrically moved with respect to the center of the planetary pin 118 by the revolution of the planetary gear 114, the grease of the outer circumference and the inner circumference of the spacer 116A can be efficiently supplied to the needle 116. That is, the planetary gears 114 can be extended in life.
再者，於滾針116之軸向O之兩端配置有用於防止滾針116向軸向O冒出並防止滾針116與輪架體120之磨損之止動部件116B。Further, at both ends of the axial direction O of the needle roller 116, a stopper member 116B for preventing the needle needle 116 from coming out in the axial direction O and preventing the needle roller 116 from being worn by the carrier body 120 is disposed.
行星銷118支承於連結輪架體板121和輪架體主體122之輪架體120。輪架體主體122藉由螺栓124締結或固定於輪架體板121。故，輪架體120與行星齒輪114之公轉成份同步而由行星銷118取出該公轉成份來旋轉。於輪架體主體122之行星齒輪相反側一體設置有法蘭形狀之輸出軸130。於該端面130A設置有多個螺栓孔132，於該螺栓孔132連結未圖示之螺栓，藉此連接對象機械150之被驅動軸。於輪架體板121及輪架體主體122之外周121A、122A配置圓錐滾子軸承126(副軸承)、128(主軸承)，從而可旋轉地支承輪架體板121及輪架體主體122。亦即，如圖1所示般，於輪架體120之半徑方向上，於行星銷118之外側配置有圓錐滾子軸承126、128。The planetary pin 118 is supported by the carrier body 120 that connects the carrier body plate 121 and the carrier body 122. The carrier body 122 is confined or fixed to the carrier body plate 121 by bolts 124. Therefore, the carrier body 120 is synchronized with the revolution component of the planetary gear 114 to be rotated by the planetary pin 118 to take out the revolution component. A flange-shaped output shaft 130 is integrally provided on the opposite side of the planetary gear of the carrier body 122. A plurality of bolt holes 132 are provided in the end surface 130A, and bolts (not shown) are coupled to the bolt holes 132, thereby connecting the driven shaft of the target machine 150. Tapered roller bearings 126 (sub-bearings) and 128 (main bearings) are disposed on the outer circumferences 121A and 122A of the carrier body plate 121 and the carrier body 122 to rotatably support the carrier body plate 121 and the carrier body 122. . That is, as shown in FIG. 1, tapered roller bearings 126, 128 are disposed on the outer side of the planetary pin 118 in the radial direction of the carrier body 120.
於圓錐滾子軸承128之外圈128C之外側配置有外殼136中之輸出側外殼138。於輸出側外殼138中，在軸向O上，於圓錐滾子軸承128之位置與所連接的對象機械150之間形成有小於圓錐滾子軸承128之外圈128C外徑d1之內徑D1部份(D1<d1)。該種大小關係基於如下者：使輸出側外殼138之外周138A與對象機械150之連接外殼152之內周152A吻合而作為與連接外殼152之內周152A嵌合而安裝時成為基準之凹窩(印籠)部E1發揮作用。故，藉由凹窩部E1可使輸出側外殼138之軸心與對象機械150之軸心於軸向O上高精密度地一致。又，藉由對象機械150之連接外殼152之端面152C與輸出側外殼138之法蘭部138B之端面138C抵接，於軸向O上進行輸出側外殼138之外周138A上的連接外殼152之定位。又，於輸出側外殼138中，於軸向O上將圓錐滾子軸承128配置於凹窩部E1之外側(圖1中為右側，或為對象機械相反側)。故，即使加大圓錐滾子軸承128亦可充分加厚到達至圓錐滾子軸承128外側之輸出側外殼138之部份138E之厚壁。亦即，輸出側外殼138可構成能夠容許施加於圓錐滾子軸承128之大轉矩的高剛性之外殼。An output side outer casing 138 of the outer casing 136 is disposed on the outer side of the outer ring 128C of the tapered roller bearing 128. In the output side casing 138, in the axial direction O, between the position of the tapered roller bearing 128 and the connected target machine 150, an inner diameter D1 portion smaller than the outer diameter d1 of the outer ring 128C of the tapered roller bearing 128 is formed. Parts (D1 < d1). This kind of size relationship is based on the fact that the outer circumference 138A of the output side casing 138 is fitted to the inner circumference 152A of the connection casing 152 of the target machine 150, and is a reference recess when fitted to the inner circumference 152A of the connection casing 152. The printing cage) part E1 plays a role. Therefore, the axis of the output side casing 138 can be aligned with the axis of the target machine 150 in the axial direction O with high precision by the dimple portion E1. Further, by the end surface 152C of the connection housing 152 of the target machine 150 abutting against the end surface 138C of the flange portion 138B of the output side housing 138, the positioning of the connection housing 152 on the outer circumference 138A of the output side housing 138 is performed in the axial direction O. . Further, in the output side casing 138, the tapered roller bearing 128 is disposed on the outer side of the dimple portion E1 in the axial direction O (the right side in FIG. 1 or the opposite side of the target machine). Therefore, even if the tapered roller bearing 128 is enlarged, the thick wall reaching the portion 138E of the output side outer casing 138 outside the tapered roller bearing 128 can be sufficiently thickened. That is, the output side outer casing 138 can constitute a high rigidity outer casing capable of allowing a large torque applied to the tapered roller bearing 128.
另一方面，於圓錐滾子軸承126之外圈126C之外側配置有外殼136中之輸入側外殼137。於輸入側外殼137包含其齒形部(內齒)134A而一體形成與行星齒輪114內接嚙合之內齒輪134。又，於輸入側外殼137中，於內齒輪134之軸向O兩側設置有避免圓錐滾子軸承126、128之(與保持圓錐滾子126B、128B之保持器之干擾而分別與其外側之)外圈126C、128C抵接之突部134B、134C。在此，於輸入側外殼137之內齒輪134之軸向O兩側配置圓錐滾子軸承126、128之外圈126C、128C。為此，於軸向O上取與圓錐滾子軸承126、突部134B、內齒輪134、突部134C、圓錐滾子軸承128並排的形態。再者，以背面組合配置有圓錐滾子軸承126、128。故，可支承高的徑向荷載和軸向荷載。On the other hand, the input side outer casing 137 of the outer casing 136 is disposed on the outer side of the outer ring 126C of the tapered roller bearing 126. The input side housing 137 includes its toothed portion (internal teeth) 134A to integrally form an internal gear 134 that is in meshing engagement with the planetary gear 114. Further, in the input side casing 137, on both sides of the axial direction O of the internal gear 134, the tapered roller bearings 126, 128 are prevented from being disposed (with the interference of the retainers of the tapered rollers 126B, 128B, respectively, and the outer side thereof) The outer rings 126C, 128C abut the protrusions 134B, 134C. Here, the outer races 126C and 128C of the tapered roller bearings 126 and 128 are disposed on both sides of the axial direction O of the inner gear 134 of the input side outer casing 137. For this purpose, the axial direction O is taken alongside the tapered roller bearing 126, the projection 134B, the internal gear 134, the projection 134C, and the tapered roller bearing 128. Further, tapered roller bearings 126 and 128 are disposed in combination with the back surface. Therefore, it can support high radial loads and axial loads.
輸入側外殼137與輸出側外殼138於軸向O上由螺栓140連結。如圖1所示般，該連結部份C設置於輸入側外殼137之內齒輪134所存在的軸向O範圍(從位置A至位置B)之外周137A。在此，因成為輸出側外殼138之內周138D覆蓋輸入側外殼137之外周137A之形態，故到達至連結部份C之輸入側外殼137之外周137A之形態部份作為輸出側外殼138與輸入側外殼137的凹窩(印籠)部E2發揮作用。故，可沿軸向O較短地實現輸入側外殼137與輸出側外殼138之連結的同時，可使輸入側外殼137之軸心和輸出側外殼138之軸心於軸向O上高精密度地一致。The input side outer casing 137 and the output side outer casing 138 are coupled by a bolt 140 in the axial direction O. As shown in FIG. 1, the joint portion C is disposed on the outer circumference 137A of the axial direction O (from the position A to the position B) in which the inner gear 134 of the input side outer casing 137 exists. Here, since the inner circumference 138D of the output side outer casing 138 covers the outer circumference 137A of the input side outer casing 137, the form portion of the outer circumference 137A of the input side outer casing 137 of the connection portion C is obtained as the output side outer casing 138 and the input. The recess (cage) portion E2 of the side outer casing 137 functions. Therefore, the connection between the input side outer casing 137 and the output side outer casing 138 can be realized in the axial direction O, and the axial center of the input side outer casing 137 and the output side outer casing 138 can be made high in the axial direction O. Consistently.
再者，內齒輪134之齒形部134A位於輸入側外殼137之端部附近。故，加工齒形部134A時，可使進行齒形加工之刀具心軸支承部更靠近被切削部(齒形部134A)，並可防止翹曲等。從而，可精度良好地加工內齒輪134之齒形部134A。Further, the toothed portion 134A of the internal gear 134 is located near the end of the input side outer casing 137. Therefore, when the tooth portion 134A is machined, the tool spindle support portion that performs the tooth profile machining can be brought closer to the workpiece portion (the tooth portion 134A), and warpage or the like can be prevented. Thereby, the toothed portion 134A of the internal gear 134 can be processed with high precision.
再者，圖1之符號142是為密封行星減速機100之內外而配置於輸出側外殼138與輪架體主體122之間之油封。Further, reference numeral 142 of FIG. 1 is an oil seal that is disposed between the output side outer casing 138 and the carrier body 122 to seal the inside and the outside of the planetary reducer 100.
接著，利用圖1、圖2對行星減速機100之裝配順序進行說明。Next, the assembly procedure of the planetary reducer 100 will be described with reference to Figs. 1 and 2 .
最先，使圓錐滾子軸承128之內圈128A和圓錐滾子128B配置於輪架體主體122之外周122A，並使輪架體主體122從對象機械相反側配置於輸出側外殼138之內側。First, the inner ring 128A of the tapered roller bearing 128 and the tapered roller 128B are disposed on the outer circumference 122A of the carrier body main body 122, and the carrier body 122 is disposed inside the output side outer casing 138 from the opposite side of the target machine.
接著，如圖2所示般，將圓錐滾子軸承128之外圈128C沿軸向O可移動地配置於輸出側外殼138之內周138D。而且，於軸向O通過內齒輪134之突部134C從對象機械相反側向對象機械側按入外圈128C的同時，將輸入側外殼137組裝於輸出側外殼138，由螺栓140使之連結而固定外圈128C和輸入側外殼137。而且，於輸入側外殼137之內周137A，於軸向O上抵接於內齒輪134之突部134B之狀態下，配置圓錐滾子軸承126之外圈126C。再者，於圖2中，已配置有油封142，但如後述亦可以於以後配置。Next, as shown in FIG. 2, the outer ring 128C of the tapered roller bearing 128 is movably disposed in the inner circumference 138D of the output side casing 138 in the axial direction O. Further, while the axial direction O is pushed into the outer ring 128C from the opposite side of the target machine toward the target machine side through the projection 134C of the internal gear 134, the input side outer casing 137 is assembled to the output side outer casing 138, and is connected by the bolt 140. The outer ring 128C and the input side outer casing 137 are fixed. Further, the outer ring 126C of the tapered roller bearing 126 is disposed in a state in which the inner circumference 137A of the input side casing 137 abuts against the projection 134B of the internal gear 134 in the axial direction O. Further, in Fig. 2, the oil seal 142 is already disposed, but it may be disposed later as will be described later.
接著，使行星銷118配置於輪架體主體122之預定位置，並使滾針116、襯墊116A、止動部件116B、行星齒輪114嵌合於該行星銷118。而且，由螺栓124安裝輪架體主體122和輪架體板121。安裝時，於輪架體板121之外周121A配置好圓錐滾子軸承126之內圈126A和圓錐滾子126B。再者，使油封142配置於輸出軸130與輸出側外殼138之間。此時，於軸向O上將墊片(未圖示)***內圈126A之對象機械相反側(於圖1中為右側)與輪架體板121之台肩部121B之間，藉此可容易地調整圓錐滾子軸承126、128之加壓。再者，***墊片之位置不限於該位置，只要是可調整圓錐滾子軸承126、128之加壓之部位則可以為任一部位。Next, the planetary pin 118 is placed at a predetermined position of the carrier body 122, and the needle 116, the spacer 116A, the stopper member 116B, and the planetary gear 114 are fitted to the planetary pin 118. Further, the carrier body main body 122 and the carrier body plate 121 are attached by bolts 124. At the time of installation, the inner ring 126A of the tapered roller bearing 126 and the tapered roller 126B are disposed on the outer circumference 121A of the carrier body plate 121. Furthermore, the oil seal 142 is disposed between the output shaft 130 and the output side outer casing 138. At this time, a spacer (not shown) is inserted in the axial direction O between the opposite mechanical side of the inner ring 126A (the right side in FIG. 1) and the shoulder portion 121B of the carrier body plate 121. The pressurization of the tapered roller bearings 126, 128 is easily adjusted. Further, the position at which the spacer is inserted is not limited to this position, and any portion may be used as long as the pressed portion of the tapered roller bearing 126, 128 can be adjusted.
接著，使壓入於未圖示之連接軸的太陽齒輪配置於行星齒輪114之內側，使用螺栓孔142由螺栓固定輸入側外殼137和可旋轉地支承該太陽齒輪之外殼部件，藉此可裝配行星減速機100。亦即，可僅從軸向O之對象機械相反側裝配行星減速機100，故容易進行裝配和修理或部件更換。又，裝配時，可以(透過未圖示之墊片等)簡單地調整圓錐滾子軸承126、128之加壓，故消除輪架體120對輸入側外殼137及輸出側外殼138之鬆動等而可維持高精密度之旋轉。又，因此亦可提高力矩剛性。Then, the sun gear that is press-fitted to the connecting shaft (not shown) is disposed inside the planetary gear 114, and the input side casing 137 and the outer casing member that rotatably supports the sun gear are bolted by the bolt holes 142, thereby being assembled Planetary reducer 100. That is, the planetary reducer 100 can be assembled only from the opposite side of the object of the axial direction O, so that assembly and repair or component replacement can be easily performed. Further, at the time of assembly, the pressurization of the tapered roller bearings 126 and 128 can be easily adjusted (by a gasket (not shown), etc., so that the looseness of the input side casing 137 and the output side casing 138 by the carrier body 120 is eliminated. Maintains high precision rotation. Moreover, the torque rigidity can also be improved.
接著，說明行星減速機100之作用。Next, the action of the planetary reducer 100 will be described.
太陽齒輪例如藉由未圖示之電動機之轉動並透過連接軸旋轉。這樣內齒輪134處於固定狀態，故行星齒輪114之公轉成份從輪架體120取出。輪架體120使安裝於輸出軸130的對象機械150之被驅動軸旋轉。The sun gear rotates through the connecting shaft by, for example, rotation of a motor (not shown). Thus, the internal gear 134 is in a fixed state, so that the revolution component of the planetary gear 114 is taken out from the carrier body 120. The carrier body 120 rotates the driven shaft of the target machine 150 mounted on the output shaft 130.
本實施形態中，將外殼136分體分割成對象機械側之輸出側外殼138和對象機械相反側之輸入側外殼137，於輸入側外殼137包含齒形部134A而一體形成內齒輪134。故，即使輸出側外殼138於圓錐滾子軸承128與對象機械之間具有小於作為主軸承的該圓錐滾子軸承128的外圈外徑d1之內徑D1部份，亦可將該圓錐滾子軸承128(從對象機械相反側)安裝於輸出側外殼138。In the present embodiment, the outer casing 136 is divided into the output side casing 138 on the object machine side and the input side casing 137 on the opposite side of the target machine, and the input side casing 137 includes the toothed portion 134A to integrally form the internal gear 134. Therefore, even if the output side outer casing 138 has a smaller inner diameter D1 than the outer diameter d1 of the outer ring of the tapered roller bearing 128 as the main bearing between the tapered roller bearing 128 and the target machine, the tapered roller can be used. A bearing 128 (opposite side from the object machine) is attached to the output side housing 138.
又，因設為如下結構，即將外殼136分體分割成輸出側外殼138和輸入側外殼137，於輸入側外殼137包含齒形部而一體形成內齒輪134，進而連結輸出側外殼138和輸入側外殼137，故可無需使行星減速機100本身大型化而配置大直徑之圓錐滾子軸承128。藉此，可加大圓錐滾子軸承128之容量，結果可使輸出轉矩或力矩剛性提高。Further, the outer casing 136 is divided into the output side casing 138 and the input side casing 137, and the input side casing 137 includes the toothed portion to integrally form the internal gear 134, and further connects the output side casing 138 and the input side. Since the outer casing 137 is provided, the large-diameter tapered roller bearing 128 can be disposed without increasing the size of the planetary reducer 100 itself. Thereby, the capacity of the tapered roller bearing 128 can be increased, and as a result, the output torque or the torque rigidity can be improved.
亦即，如先前技術般，將內齒輪與外殼設為分體結構時，或者即便將內齒輪與外殼設為一體結構，當將內齒輪與其齒形部設為分體結構時，為將內齒輪或齒形部固定於外殼，必須縮小沿軸向O與外殼之內齒輪或齒形部鄰接之部份，亦即支承外殼之主軸承的部份之內徑，結果存在或縮小主軸承之直徑，或若不縮小主軸承之直徑，則行星減速機本身被大型化之問題。That is, as in the prior art, when the internal gear and the outer casing are in a separate structure, or even if the internal gear and the outer casing are integrally formed, when the internal gear and the toothed portion thereof are provided as a separate structure, The gear or the toothed portion is fixed to the outer casing, and the portion adjacent to the inner gear or the toothed portion of the outer casing, that is, the inner diameter of the portion of the main bearing supporting the outer casing, must be reduced, and the main bearing is present or reduced. The diameter, or if the diameter of the main bearing is not reduced, the planetary reducer itself is enlarged.
與此相反，本實施形態藉由具有上述結構，無需縮小沿軸向O與外殼136之內齒輪134鄰接的部份之內徑D1，故可無需使行星減速機100本身大型化而將大直徑之圓錐滾子軸承128作為主軸承來配置。其結果，可加大主軸承之容量並可使輸出轉矩及力矩剛性提高。On the other hand, in the present embodiment, since the inner diameter D1 of the portion adjacent to the inner gear 134 of the outer casing 136 in the axial direction O is not required to be reduced, the large diameter of the planetary reducer 100 itself can be increased without increasing the size of the planetary reducer 100 itself. The tapered roller bearing 128 is configured as a main bearing. As a result, the capacity of the main bearing can be increased and the output torque and torque rigidity can be improved.
又，因將輸入側外殼137與輸出側外殼138之連結部份C設置於輸入側外殼137之內齒輪134所存在的軸向O範圍之外周137A，故可使到達至該連結部份C之輸入側外殼137之外周137A之形態部份作為輸出側外殼138與輸入側外殼137之凹窩部E2發揮作用。為此，可使輸入側外殼137和輸出側外殼138各自之軸心與軸向O高精密度地一致，故行星減速機100可長期實現無軸擺動之順利的旋轉。同時，可沿軸向O較短地實現輸入側外殼137與輸出側外殼138之連結並可縮短行星減速機100之軸向長度。Further, since the connecting portion C of the input side outer casing 137 and the output side outer casing 138 is disposed outside the outer circumference 137A of the axial direction O where the internal gear 134 of the input side outer casing 137 exists, it is possible to reach the connecting portion C. The form portion of the outer circumference 137A of the input side outer casing 137 functions as the output side outer casing 138 and the dimple portion E2 of the input side outer casing 137. For this reason, the axis of each of the input side outer casing 137 and the output side outer casing 138 can be aligned with the axial direction O with high precision, so that the planetary reducer 100 can smoothly rotate without shaft swing for a long period of time. At the same time, the connection between the input side outer casing 137 and the output side outer casing 138 can be realized in the axial direction O and the axial length of the planetary reducer 100 can be shortened.
又，輸出側外殼138之外周138A作為與對象機械150之連接外殼152之內周152A嵌合而安裝時成為基準之凹窩部E1發揮作用，故易進行對象機械150與行星減速機100之對軸。Further, since the outer circumference 138A of the output side casing 138 functions as a reference recessed portion E1 when it is fitted to the inner circumference 152A of the connection casing 152 of the target machine 150, it is easy to perform the pair of the target machine 150 and the planetary reducer 100. axis.
又，圓錐滾子軸承128配置於比行星銷118更靠輪架體120之半徑方向外側，故可進一步加大圓錐滾子軸承128。故，可進一步增大施加於輪架體120的徑向荷載之容量。Further, since the tapered roller bearing 128 is disposed on the outer side in the radial direction of the carrier body 120 than the planetary pin 118, the tapered roller bearing 128 can be further enlarged. Therefore, the capacity of the radial load applied to the carrier body 120 can be further increased.
又，具備作為副軸承的圓錐滾子軸承126，該圓錐滾子軸承於軸向O上相對於內齒輪134將構成輪架體120之輪架體板121支承於圓錐滾子軸承128之相反側，故可設為更大的輸出轉矩。同時，因可使輪架體120之軸心與軸向O高精密度地一致，故可順利地保持輪架體120之旋轉。而且，以背面組合使用圓錐滾子軸承126、128，故可支承高的徑向荷載和軸向荷載。Further, a tapered roller bearing 126 as a sub-bearing is provided which supports the carrier body plate 121 constituting the carrier body 120 on the opposite side of the tapered roller bearing 128 with respect to the internal gear 134 in the axial direction O Therefore, it can be set to a larger output torque. At the same time, since the axis of the carrier body 120 can be aligned with the axial direction O with high precision, the rotation of the carrier body 120 can be smoothly maintained. Moreover, the tapered roller bearings 126, 128 are used in combination with the back side, so that high radial loads and axial loads can be supported.
又，於本實施形態中，輪架體120成為連結分別支承於圓錐滾子軸承126、128的輪架體板121和輪架體主體122之結構。而且，圓錐滾子軸承126、128之內圈126A、128A分別配置於輪架體板121之外周121A、輪架體主體122之外周122A。圓錐滾子軸承128之外圈128C配置於輸出側外殼138之內周138D，以使在連結輸出側外殼138和輸入側外殼137時於軸向O上固定。又，圓錐滾子軸承126之外圈126C配置於輸入側外殼137之內周137A。故，於連結輪架體板121和輪架體主體122時，於軸向O上，於圓錐滾子軸承126之內圈126A之對象機械相反側(於圖1中為右側)與輪架體板121之台肩部121B之間***墊片等，藉此可易調整圓錐滾子軸承126、128之加壓。因此，可消除輪架體120對外殼136之鬆動而維持高精密度的旋轉。又，為此亦能夠提高力矩剛性。Further, in the present embodiment, the carrier body 120 is configured to connect the carrier body plate 121 and the carrier body 122 that are supported by the tapered roller bearings 126 and 128, respectively. Further, the inner rings 126A and 128A of the tapered roller bearings 126 and 128 are respectively disposed on the outer circumference 121A of the carrier body plate 121 and the outer circumference 122A of the carrier body 122. The outer ring 128C of the tapered roller bearing 128 is disposed on the inner circumference 138D of the output side outer casing 138 so as to be fixed in the axial direction O when the output side outer casing 138 and the input side outer casing 137 are joined. Further, the outer ring 126C of the tapered roller bearing 126 is disposed on the inner circumference 137A of the input side casing 137. Therefore, when the carrier body plate 121 and the carrier body 122 are coupled, in the axial direction O, the opposite side of the mechanical ring (the right side in FIG. 1) of the inner ring 126A of the tapered roller bearing 126 and the carrier body A gasket or the like is inserted between the shoulder portions 121B of the plate 121, whereby the pressurization of the tapered roller bearings 126, 128 can be easily adjusted. Therefore, the rotation of the carrier body 120 to the outer casing 136 can be eliminated to maintain high-precision rotation. Moreover, the torque rigidity can also be improved for this purpose.
從而，根據本實施形態，可無需使行星減速機100本身大型化而採用大直徑之圓錐滾子軸承128，故可加大作為主軸承的圓錐滾子軸承128之容量並能使輸出轉矩及力矩剛性提高。Therefore, according to the present embodiment, the large-diameter tapered roller bearing 128 can be used without increasing the size of the planetary reducer 100 itself, so that the capacity of the tapered roller bearing 128 as the main bearing can be increased and the output torque can be made. The torque rigidity is increased.
舉第1實施形態對本發明進行了說明，但本發明係不限於第1實施形態者。亦即，可進行不脫離本發明宗旨之範圍內之改良及設計之變更是不言而喻的。Although the present invention has been described in the first embodiment, the present invention is not limited to the first embodiment. In other words, it is self-evident that modifications and design changes can be made without departing from the spirit and scope of the invention.
例如，於第1實施形態中，輸出軸130為法蘭形狀，但本發明不限於此，根據對象機械之被驅動軸之形狀容易變更輸出軸之形狀。例如，如圖3之第2實施形態所示般，亦可於輪架體主體222設置圓柱形狀之輸出軸230，透過鍵槽230A與對象機械250之被驅動軸連接。再者，該種所謂對實心類型之輸出軸之變更(第1實施形態稱為法蘭類型)可僅由不損害本發明之作用效果而構成輸出軸之部件(輪架體和輸出軸，或者輸出軸之追加)之變更來容易進行。亦即，因可謀求構成輸出軸的部件以外的共同化，故可謀求具備法蘭類型或實心類型之輸出軸的行星減速機之低成本化。For example, in the first embodiment, the output shaft 130 has a flange shape. However, the present invention is not limited thereto, and the shape of the output shaft can be easily changed depending on the shape of the driven shaft of the target machine. For example, as shown in the second embodiment of FIG. 3, a cylindrical output shaft 230 may be provided in the carrier body 222, and may be connected to the driven shaft of the target machine 250 through the key groove 230A. Further, this type of change to the output shaft of the solid type (referred to as the flange type in the first embodiment) can constitute the member of the output shaft (the carrier body and the output shaft, or the like, without impairing the effects of the present invention, or The change of the output axis is easy to change. In other words, since it is possible to achieve commonalization other than the components constituting the output shaft, it is possible to reduce the cost of the planetary reducer including the flange type or the solid type of output shaft.
又，於上述實施形態中，固定外殼而於輪架體設置輸出軸，但本發明未必限定於此，亦可以為固定輪架體並旋轉外殼而獲得輸出的所謂框旋轉類型。Further, in the above embodiment, the output case is fixed to the carrier body by the outer casing. However, the present invention is not limited thereto, and a so-called frame rotation type in which the output of the carrier body is fixed and the outer casing is rotated to obtain an output may be employed.
又，於上述實施形態中，以背面組合使用了2個圓錐滾子軸承，但本發明未必限定於此，亦可以為使用1個軸承之情況。例如可以僅於圖1之圓錐滾子軸承(主軸承)128之位置配置交叉滾子軸承而使用。此時，也可以於對象機械之被驅動軸之軸向上負擔雙方向之軸向荷載，並可獲得與使用2個圓錐滾子軸承時相同的作用效果，進而可實現行星減速機沿軸向O之縮短。Further, in the above embodiment, two tapered roller bearings are used in combination with the back surface. However, the present invention is not limited thereto, and one bearing may be used. For example, a cross roller bearing may be disposed only at the position of the tapered roller bearing (main bearing) 128 of Fig. 1 . At this time, it is also possible to bear the axial load in both directions in the axial direction of the driven shaft of the target machine, and the same effect as that in the case of using two tapered roller bearings can be obtained, and the planetary reducer can be realized along the axial direction. Shortened.
又，使用2個軸承時，不僅可以使用圓錐滾子軸承，亦可以使用角接觸軸承(滾子或球)，其組合亦並不限於背面，亦可以為正面組合或並列組合。Further, when two bearings are used, not only tapered roller bearings but also angular contact bearings (rollers or balls) may be used, and the combination is not limited to the back surface, and may be a front combination or a side combination.
又，於上述實施形態中，行星減速機為簡單行星齒輪機構，但本發明未必限定於此。例如行星齒輪可以為由偏心體之旋轉進行擺動旋轉之外齒輪。此時，行星銷(輪架銷)與外齒輪之自轉成份同步，從該行星銷取出外齒輪之自轉成份。當然，此時亦可以設為外殼旋轉的框旋轉類型。Further, in the above embodiment, the planetary reducer is a simple planetary gear mechanism, but the present invention is not necessarily limited thereto. For example, the planetary gear may be a gear that is oscillated by the rotation of the eccentric body. At this time, the planetary pin (wheel pin) is synchronized with the rotation component of the external gear, and the rotation component of the external gear is taken out from the planetary pin. Of course, it is also possible to set the frame rotation type in which the outer casing rotates.
100、200．．．行星減速機100, 200. . . Planetary reducer
114、214．．．行星齒輪114,214. . . Planetary gear
116、216．．．滾針116,216. . . Needle roller
118、218．．．行星銷118,218. . . Planetary pin
120、220．．．輪架體120, 220. . . Wheel frame
121、221．．．輪架體板121, 221. . . Wheel frame
122、222．．．輪架體主體122, 222. . . Wheel body
126、128、226、228．．．圓錐滾子軸承126, 128, 226, 228. . . Tapered Roller Bearings
126A、128A．．．內圈126A, 128A. . . Inner ring
126B、128B．．．圓錐滾子126B, 128B. . . Tapered roller
126C、128C．．．外圈126C, 128C. . . Outer ring
130、230．．．輸出軸130, 230. . . Output shaft
134、234．．．內齒輪134, 234. . . Internal gear
134A．．．齒形部(內齒)134A. . . Toothed part (internal tooth)
136、236．．．外殼136, 236. . . shell
137、237．．．輸入側外殼137, 237. . . Input side housing
138、238．．．輸出側外殼138, 238. . . Output side housing
150、250．．．對象機械150, 250. . . Object machinery
152、252．．．連接外殼152, 252. . . Connection housing
圖1係表示本發明之第1實施形態所涉及的行星減速機之主要部份之一例的剖視示意圖。Fig. 1 is a schematic cross-sectional view showing an example of a main part of a planetary reducer according to a first embodiment of the present invention.
圖2同樣為連結外殼和輸入側外殼時之剖視示意圖。Fig. 2 is also a schematic cross-sectional view showing the case where the outer casing and the input side casing are joined.
圖3係表示本發明之第2實施形態所涉及的行星減速機之主要部份之一例的剖視示意圖。Fig. 3 is a schematic cross-sectional view showing an example of a main part of a planetary reducer according to a second embodiment of the present invention.
100．．．行星減速機100. . . Planetary reducer
134A．．．齒形部134A. . . Toothed part
142．．．油封142. . . Oil seal
137．．．輸入側外殼137. . . Input side housing
126B．．．圓錐滾子126B. . . Tapered roller
126C、128C．．．外圈126C, 128C. . . Outer ring
134B、134C．．．突部134B, 134C. . . Projection
126．．．圓錐滾子軸承126. . . Tapered Roller Bearings
126A．．．內圈126A. . . Inner ring
121B．．．台肩部121B. . . Shoulder
121．．．輪架體板121. . . Wheel frame
116．．．滾針116. . . Needle roller
130A．．．輸出軸之端面130A. . . End face of the output shaft
114．．．行星齒輪114. . . Planetary gear
128B．．．圓錐滾子128B. . . Tapered roller
118．．．行星銷118. . . Planetary pin
116A．．．襯墊116A. . . pad
116B．．．止動部件116B. . . Stop member
124、140．．．螺栓124, 140. . . bolt
121A、137A．．．外周121A, 137A. . . Peripheral
136．．．外殼136. . . shell
138D．．．內周138D. . . Inner week
138E．．．圓錐滾子軸承之外側之輸出側外殼之部份138E. . . Part of the output side housing on the outside of the tapered roller bearing
137A(E2)．．．外周137A (E2). . . Peripheral
120．．．輪架體120. . . Wheel frame
150．．．對象機械150. . . Object machinery
122A．．．輪架體主體之外周122A. . . Outside the body of the wheel frame body
122．．．輪架體主體122. . . Wheel body
130．．．輸出軸130. . . Output shaft
128A．．．內圈128A. . . Inner ring
132．．．螺栓孔132. . . Bolt hole
152A．．．連接外殼之內周152A. . . Connecting the inner circumference of the outer casing
138A(E1)．．．外周138A (E1). . . Peripheral
152．．．連接外殼152. . . Connection housing
128．．．圓錐滾子軸承128. . . Tapered Roller Bearings
138C．．．端面138C. . . End face
152C．．．端面152C. . . End face
138B．．．法蘭部138B. . . Flange
138．．．輸出側外殼138. . . Output side housing
134．．．內齒輪134. . . Internal gear
D1．．．圓錐滾子軸承之外圈之內徑D1. . . The inner diameter of the outer ring of tapered roller bearing
d1．．．圓錐滾子軸承之外圈之外徑D1. . . Tapered roller bearing outer ring outer diameter
O．．．軸向O. . . Axial
A、B、C．．．位置A, B, C. . . position
G．．．間隙G. . . gap
Claims (5)
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009203606A JP5528744B2 (en) | 2009-09-03 | 2009-09-03 | Planetary reducer |
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| Publication Number | Publication Date |
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| TW201109548A TW201109548A (en) | 2011-03-16 |
| TWI404872B true TWI404872B (en) | 2013-08-11 |
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| Application Number | Title | Priority Date | Filing Date |
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| TW099129695A TWI404872B (en) | 2009-09-03 | 2010-09-02 | Planetary reducer |
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| JP (1) | JP5528744B2 (en) |
| KR (1) | KR101248388B1 (en) |
| CN (1) | CN102011858B (en) |
| DE (1) | DE102010036063B4 (en) |
| TW (1) | TWI404872B (en) |
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| CN102518787A (en) * | 2011-12-13 | 2012-06-27 | 哈尔滨东安发动机（集团）有限公司 | Planetary transmission structure of wind power gear box |
| JP5917422B2 (en) | 2013-01-30 | 2016-05-11 | 住友重機械工業株式会社 | Decelerator |
| JP2017053461A (en) * | 2015-09-10 | 2017-03-16 | 株式会社ハーモニック・ドライブ・システムズ | Planetary gear train |
| TWI609143B (en) | 2016-12-29 | 2017-12-21 | 財團法人工業技術研究院 | Eccentric oscillating speed reducer |
| CN108167396A (en) * | 2017-12-27 | 2018-06-15 | 北奔重型汽车集团有限公司 | A kind of five wheeled helical gear planetary reduction gear structure of drive axle |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN1478183A (en) * | 2000-12-22 | 2004-02-25 | ������˹�۳��ֹ����ɷݹ�˾ | Planetary gear device |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US4091688A (en) | 1976-09-01 | 1978-05-30 | Dana Corporation | Easily assembled and disassembled planetary gear assembly |
| TW334500B (en) | 1994-06-16 | 1998-06-21 | Sumitomo Heavy Industries | Series of geared motor |
| US6129648A (en) | 1997-11-19 | 2000-10-10 | Harmonic Drive Systems, Inc. | Planetary gear device |
| JP2000257675A (en) * | 1999-03-08 | 2000-09-19 | Kadowaki:Kk | Planetary gear speed reducer and manufacturing apparatus therefor |
| JP4353735B2 (en) * | 2003-06-20 | 2009-10-28 | 株式会社ハーモニック・ドライブ・システムズ | Planetary gear set |
| JP2005233206A (en) * | 2004-02-17 | 2005-09-02 | Nidec-Shimpo Corp | Bearing structure |
| JP4477404B2 (en) * | 2004-04-15 | 2010-06-09 | 株式会社テイエルブイ | Tag device |
| DE202004016131U1 (en) * | 2004-10-18 | 2006-02-23 | Zae-Antriebssysteme Gmbh & Co. | Control drive for pressure or aligning rollers in coating device, has driving and driven sun gear teeth slightly and circumferentially deviated from each other while meshed into corresponding planetary gears |
| JP2006258270A (en) * | 2005-03-18 | 2006-09-28 | Nidec-Shimpo Corp | Supporting structure of turning member in planetary gear reducer |
| JP5150136B2 (en) * | 2007-05-17 | 2013-02-20 | オリエンタルモーター株式会社 | Planetary gear set |
| JP5093892B2 (en) | 2008-02-26 | 2012-12-12 | キャタピラー エス エー アール エル | Cover locking device |
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| CN1478183A (en) * | 2000-12-22 | 2004-02-25 | ������˹�۳��ֹ����ɷݹ�˾ | Planetary gear device |
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| Publication number | Publication date |
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| CN102011858B (en) | 2015-07-01 |
| CN102011858A (en) | 2011-04-13 |
| KR20110025079A (en) | 2011-03-09 |
| DE102010036063A1 (en) | 2011-04-07 |
| JP5528744B2 (en) | 2014-06-25 |
| JP2011052785A (en) | 2011-03-17 |
| DE102010036063B4 (en) | 2020-12-17 |
| TW201109548A (en) | 2011-03-16 |
| KR101248388B1 (en) | 2013-03-28 |
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