CN104948720A - Rotation device - Google Patents
Rotation device Download PDFInfo
- Publication number
- CN104948720A CN104948720A CN201510039594.1A CN201510039594A CN104948720A CN 104948720 A CN104948720 A CN 104948720A CN 201510039594 A CN201510039594 A CN 201510039594A CN 104948720 A CN104948720 A CN 104948720A
- Authority
- CN
- China
- Prior art keywords
- whirligig
- bearing
- oil sealing
- axle
- input shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000007789 sealing Methods 0.000 claims description 66
- 238000005461 lubrication Methods 0.000 claims description 45
- 239000008041 oiling agent Substances 0.000 claims description 44
- 239000003638 chemical reducing agent Substances 0.000 claims description 23
- 230000002093 peripheral effect Effects 0.000 claims description 11
- 239000007788 liquid Substances 0.000 claims description 10
- 230000001050 lubricating effect Effects 0.000 abstract description 4
- 230000009467 reduction Effects 0.000 abstract description 4
- 239000000314 lubricant Substances 0.000 abstract description 3
- 238000010408 sweeping Methods 0.000 description 10
- 230000010355 oscillation Effects 0.000 description 7
- 238000005096 rolling process Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 230000003321 amplification Effects 0.000 description 3
- 238000003199 nucleic acid amplification method Methods 0.000 description 3
- 239000000428 dust Substances 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 230000035515 penetration Effects 0.000 description 2
- 102220477731 Tumor necrosis factor receptor superfamily member 13C_L28A_mutation Human genes 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000007598 dipping method Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 239000004519 grease Substances 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000007790 scraping Methods 0.000 description 1
- 238000003756 stirring Methods 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
- 230000007306 turnover Effects 0.000 description 1
- 230000003442 weekly effect Effects 0.000 description 1
Classifications
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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
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0467—Elements of gearings to be lubricated, cooled or heated
- F16H57/0469—Bearings or seals
- F16H57/0472—Seals
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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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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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
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/029—Gearboxes; Mounting gearing therein characterised by means for sealing the gearboxes, e.g. to improve airtightness
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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
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0401—Features relating to lubrication or cooling or heating using different fluids, e.g. a traction fluid for traction gearing and a lubricant for bearings or reduction gears
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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
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
- F16H57/0424—Lubricant guiding means in the wall of or integrated with the casing, e.g. grooves, channels, holes
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Details Of Gearings (AREA)
- Sealing With Elastic Sealing Lips (AREA)
- Retarders (AREA)
- Mounting Of Bearings Or Others (AREA)
- Sealing Of Bearings (AREA)
Abstract
The project of the invention is to obtain a rotation device which can further improve lubricity of oil seal. A reduction gear is the rotation device (12), comprising a housing (34) which is sealed with a lubricant, the housing being a cover housing (54), an input shaft (18), and oil seal (72). The oil seal is configured on the axial outer side which is closer to the input shaft than an input bearing (60). Axial movement of the input bearing is limited by a check ring (74). The check ring is embedded in a check ring groove (54A) on the inner side which is closer to the reduction gear than the position of the input bearing. The housing is provided with a lubricating channel (78) on the radial outer side of the input bearing. The lubricating channel communicates a space which is closer to the inner side of the reduction gear than the input bearing and the oil seal. The lubricating channel is provided with an inclined surface (78D) which is inclined relative to the input shaft. the tail end (78D2) of the inclined surface is closer to the oil seal side on the axial direction than the position of the check ring.
Description
The application advocates the preference of No. 2014-060986th, the Japanese patent application based on application on March 24th, 2014.The full content of this Japanese publication is by reference to being applied in this specification.
Technical field
The present invention relates to a kind of whirligig.
Background technique
Disclose a kind of power transmitting deice (whirligig) in patent documentation 1, it possesses the shell being sealed with oiling agent and the high speed shaft running through this shell.
In this power transmitting deice, between high speed shaft and shell, be configured with the bearing of this high speed shaft of supporting.The oil sealing of the oiling agent in can is configured with between the high speed shaft and shell in the axially outside of this bearing.
Patent documentation 1: Japanese Unexamined Patent Publication 2011-043243 publication (Fig. 8)
But in the whirligig of this structure, because oil sealing is configured at the axially outside of (being embedded between high speed shaft and shell) bearing, the lubrication that therefore there is the sealing labial surface of this oil sealing easily becomes insufficient problem.
Summary of the invention
The present invention completes to solve this problem in the past, and its problem is to provide a kind of whirligig that can improve the lubricity of oil sealing further.
The present invention solves above-mentioned problem by being set to following structure, a kind of whirligig, it possesses: the shell being sealed with oiling agent, run through the axle of this shell, be configured at bearing and the oil sealing of the described axle between this axle and shell, wherein, described oil sealing is configured at than described bearing more by the axially outside of described axle, moving axially of described bearing is limited by back-up ring, described back-up ring is more leaning on the private side of described whirligig to be embedded in the circlip groove of described shell than described bearing, described shell has lubrication channel at the radial outside of described bearing, between the space that this lubrication channel is communicated with the private side more leaning on described whirligig than this bearing and described oil sealing, this lubrication channel has the plane of inclination tilted relative to described axle, the end of this plane of inclination is presented axially in than described back-up ring more by described oil sealing side.
In the present invention, shell has the lubrication channel between space and oil sealing being communicated with the private side more leaning on whirligig than this bearing at the radial outside of bearing.Therefore, oiling agent, by this lubrication channel, can be walked around bearing and arrive oil sealing.
Further, lubrication channel has the plane of inclination tilted relative to axle, and the end of this plane of inclination is presented axially in than described back-up ring more by described oil sealing side.Therefore, oiling agent can arrive the oil sealing side of back-up ring effectively along this plane of inclination.Further, oiling agent is stopped by this back-up ring, prevents oiling agent from getting back to the private side of whirligig thus, can more effectively lubricate oil sealing.
According to the present invention, obtain the whirligig that can improve the lubricity of oil sealing further.
Accompanying drawing explanation
Fig. 1 is the overall sectional view of the whirligig involved by an example of embodiments of the present invention.
Fig. 2 is the major component amplification view of Fig. 1.
Fig. 3 is the sectional view of the arrow III-III line along Fig. 2.
Fig. 4 is the major component amplification view of the whirligig involved by an example of another embodiment of the present invention.
In figure: 12-speed reducer (whirligig), 14-internal gear, 16-external gear, 18-input shaft (axle), 28-eccentric body, 34-shell, 54-cover body shell, 54A-circlip groove, 60-input shaft bearing, 72-oil sealing, 74-back-up ring, 78-lubrication channel, 78D-plane of inclination.
Embodiment
Below, with reference to the accompanying drawings an example of embodiments of the present invention is described in detail.
Fig. 1 is the overall sectional view of the eccentric oscillating-type speed reducer (whirligig) involved by an example of embodiments of the present invention, and Fig. 2 is the major component amplification view of Fig. 1, and Fig. 3 is the sectional view of the arrow III-III line along Fig. 2.
This speed reducer (whirligig) 12 possesses the shell 34 being sealed with oiling agent and the input shaft 18 running through this shell 34.Speed reducer 12 involved by present embodiment is for possessing the eccentric oscillating-type speed reducer as lower component: internal gear 14; External gear 16, with this internal gear 14 internal messing while swing; Axle, has the eccentric body 28 for making this external gear 16 swing.The input shaft 18 of this speed reducer 12 is equivalent to " axle " in present embodiment.
Below, the structure of speed reducer 12 is described successively from input side.
Input shaft 18 is via key (only illustrating keyway 18A) and the link such as not shown motor drive shaft or belt wheel.Input shaft 18 is linked with the starting of oscillation parts 30 possessing 2 eccentric bodies 28 via key 26.The periphery of each eccentric body 28 is relative to the axle center C18 only eccentric eccentric amount e (with reference to figure 2) of input shaft 18.2 eccentric bodies 28 eccentric phase difference 180 degree (to diametrically mutual away from direction bias).External gear 16 can be assembled with rotatably by eccentric swing via eccentric body bearing 32 in the periphery of eccentric body 28.With internal gear 14 internal messing while external gear 16 swings.
In this mode of execution, internal gear 14 is formed primarily of such as lower component: internal gear main body 14A, and it is integrated with shell 34; Rest pin 14B, is supported on this internal gear main body 14A; And outer roller 14C, be rotatably assembled in the periphery of this rest pin 14B, and form the internal tooth of internal gear 14.The interior number of teeth (quantity of outer roller 14C) of internal gear 14 is slightly more than the outer number of teeth (in this example only many 1) of external gear 16.
The vibrating part 36 forming the part exporting body 46 is configured with in the axial side (load side) of external gear 16.Vibrating part 36 is formed with press-in hole 36A, is fitted together to by press-in in this press-in hole 36A, be linked with pin parts 38.These pin parts 38 run through the penetration hole 16A being arranged at external gear 16.In the periphery of pin parts 38, chimeric (outer) has roller member 40 slidably.Guarantee to have the gap of 2 times of the eccentric amount e being equivalent to eccentric body 28 between the penetration hole 16A of roller member 40 and external gear 16.
The intermediate member 42 that vibrating part 36 reduces with 4 stages via the diameter of axle is integrated with the output shaft assembly 44 that the diameter of axle reduces further.Roller member 40, pin parts 38, vibrating part 36, intermediate member 42 and output shaft assembly 44 are integrally formed the larger output body 46 of rotation.Export body 46 and be rotatably freely supported on shell 34 via output bearing 48,50.
Shell 34 is formed primarily of such as lower component: housing main body 53; Cover body shell 54, supports described input shaft 18 in the load reverse side of housing main body 53; Sidepiece shell 56, supports described output body 46 in the load side of housing main body 53; End enclosure 58, closes the axial end portion of this sidepiece shell 56.That is, cover body shell 54 forms a part for the shell 34 of speed reducer 12.
Input shaft 18 is supported by the input shaft bearing 59 of the input shaft bearing 60 that is supported on the load reverse side of this cover body shell 54 and the load side that is supported on described vibrating part 36.The input shaft bearing 60 of load reverse side is equivalent to " bearing " of the present invention.
Symbol 70 represents the oil sealing of the outlet side (load side) of the oiling agent be used in can 34, and symbol 72 represents the oil sealing of input side (load reverse side).In present embodiment, the present invention is applicable to the lubrication of the oil sealing 72 of input side.In addition, about oiling agent, adopt oil (lubricant oil) in this embodiment, but such as can also use lubricating grease etc.
Below, the structure near the oil sealing 72 of input side is described in detail.
In this mode of execution, input shaft bearing 60 is made up of the ball bearing with outer ring 60A, inner ring 60B and rolling element 60C.Input shaft bearing 60 is the so-called stuffing box bearing that oil sealing 72 side of rolling element 60C is shielded by sealed member 60D.
Input shaft bearing 60 is limited to axial device private side (to load side) mobile by back-up ring 74.Back-up ring 74 is more leaning on the private side of speed reducer 12 than this input shaft bearing 60, be embedded in the circlip groove 54A being formed in (part for formation shell 34) cover body shell 54, thus be fixed in the axial direction.
Oil sealing 72 is configured at than input shaft bearing 60 more by the axially outside (outer side of speed reducer 12) of input shaft 18.This is because, while needing can to lubricate (being positioned at than oil sealing 72 more by axial inner side) input shaft bearing 60 with the oiling agent in shell 34 by seals lubricant at this shell 34.The oil sealing 72 of this mode of execution has: primary seal lip 72B, possesses spring 72A; Dust excluder lips 72C, is configured at the axial device outer side of primary seal lip 72B.
The position press-in being equivalent to the radially inner side of oil sealing 72 of input shaft 18 has axle sleeve 76, and the primary seal lip 72B of oil sealing 72 and dust excluder lips 72C sealing labial surface 72B1,72C1 separately abut with the periphery of this axle sleeve 76, the oiling agent thus in can 34.In addition, axle sleeve 76 abuts with the inner ring 60B of input shaft bearing 60, limits this input shaft bearing 60 mobile to axial device outer side (to load reverse side).
In this mode of execution, oiling agent is enclosed to the position (highly) roughly the same with the foot 60A1 of the outer ring 60A inner circumferential of input shaft bearing 60.That is, the position of the liquid level Li1 of oiling agent is lower than the position of sealing labial surface 72B1,72C1 of oil sealing 72.The position of the liquid level Li1 of oiling agent is suppressed to be for so low reason, as present embodiment, when speed reducer is the speed reducer (whirligig) 12 of the structure with eccentric body 28 eccentric swing, if this eccentric body 28 or eccentric body bearing 32 etc. are more submerged in oiling agent, then the resistance of eccentric swing becomes very large.In addition, the position of the liquid level Li1 of this oiling agent is set to as follows, and namely the peripheral part 28A of eccentric body 28 or the retainer 32A of eccentric body bearing 32 etc. can not immerse when eccentric body 28 is eccentric upward, and immerses time eccentric downwards.In other words, such as can be understood as, eccentric body 28 plays function as gomphosis part, described gomphosis part has peripheral part 28A, and external diameter (profile) L28A of described peripheral part 28A is greater than the distance L of axle center C18 to the liquid level Li1 of oiling agent (C18-Li1) from input shaft 18.
On the other hand, cover body shell 54 has at the radial outside of input shaft bearing 60 lubrication channel 78,79 between space (the space P1 in shell 34) and oil sealing 72 being communicated with the private side more leaning on speed reducer 12 than this input shaft bearing 60.Specifically, in this mode of execution, be formed with 2 place's lubrication channels in the circumferential altogether, namely be formed with the lubrication channel 78 with plane of inclination 78D described later in the upside (radial outside) of the input shaft bearing 60 of cover body shell 54 part, in the downside (radial outside) of input shaft bearing 60, part is formed with the lubrication channel 79 (with reference to figure 3) without plane of inclination.
As shown in Figure 3, the square with the axis section of the lubrication channel 78 of upside is formed as reverse U shape.This shape such as can be formed by general purpose tools such as not shown end mills (mold can also be utilized to be formed, thus omit machining).The circular arc 78C that the section on the top of reverse U shape is r78C by radius is formed.The single dotted broken line of Fig. 2 represents the circumferential position axially of the center C78C of this circular arc 78C.
As shown in Figure 2, the lubrication channel 78 of upside has the plane of inclination 78D tilted relative to input shaft 18 (axle center C18).Specifically, plane of inclination 78D is relative to the axle center C18 only cant angle theta 78D of input shaft 18, diminish from axle center C18 size L78D of (specifically, to the topmost part of the circular arc 78C on each axial position) to the 78D of plane of inclination of this input shaft 18 along with towards axial outside (device outer side: load reverse side).
Corresponding, the lubrication channel 78 in cover body shell 54 be formed radially width W 78 also and uneven, near the top 78D1 (entrance of lubrication channel 78) of plane of inclination 78D, the width W 78 that is formed radially of lubrication channel 78 is maximum W78D1.Further, near the end 78D2 of plane of inclination 78D, the width W 78 that is formed radially of lubrication channel 78 is (being less than W78D1's) W78D2 (W78D1 > W78D2).In addition, in this mode of execution, the end 78D2 of plane of inclination 78D refers to " angle being with the axle center C18 of input shaft 18 is less than the face (inner peripheral surface of channel outlet port 78E described later) of the angle theta 78D that plane of inclination 78D and this axle center C18 is and the tie point of this plane of inclination 78D ".
The top 78D1 of plane of inclination 78D to be positioned at than back-up ring 74 position of the more close size L (78D1-74) to the side contrary with oil sealing, and the end 78D2 of plane of inclination 78D to be positioned at than back-up ring 74 position of the more close size L (78D2-74) to oil sealing 72 side.That is, the top 78D1 of plane of inclination 78D is positioned at than back-up ring 74 more by the position with oil sealing opposite side, and the end 78D2 of plane of inclination 78D is positioned at than back-up ring 74 more by the position of oil sealing 72 side.
In addition, the lubrication channel 78 in axially outside is more leaned on to be formed along the periphery of the outer ring 60A of input shaft bearing 60 and form channel outlet port 78E than the end 78D2 of plane of inclination 78D.The center C78C of " the circular arc 78C " of this channel outlet port 78E more enters radially inner side than the external diameter of the outer ring 60A of input shaft bearing 60.That is, the circular arc 78C of the channel outlet port 78E of lubrication channel 78 is less than semicircle (half cycle) (circular arc (78C) with reference to the downside of figure 3).In addition, L (78F-74) is of a size of till back-up ring 74 and the end 78F of lubrication channel 78.
Oil sealing 72 is configured to, and more enters dimension delta L72 to (device private side) in lubrication channel 78 than the end 78F of this lubrication channel 78, more effectively can accept the oiling agent come along lubrication channel 78.
In addition, the lubrication channel 79 of downside also has the structure identical with the lubrication channel 78 of above-mentioned upside.But, in the lubrication channel 79 of downside, due to without the need to having the function guided to oil sealing 72 side by accepted oiling agent (spittle), be not therefore formed with (lubrication channel 78 on the upside of being formed at) described plane of inclination 78D.
In addition, symbol 80 is configured at the axle sleeve between the inner ring 60B of input shaft bearing 60 and starting of oscillation parts 30 (eccentric body 28).
Then, the effect of this eccentric oscillating-type speed reducer 12 is described.
If the input shaft 18 of speed reducer 12 is rotated by the rotation of not shown motor drive shaft, then the starting of oscillation parts 30 linked via key 26 and input shaft 18 rotate.If starting of oscillation parts 30 rotate, then the eccentric body 28 be integrally formed with these starting of oscillation parts 30 rotates.
If eccentric body 28 rotates, then via eccentric body bearing 32, external gear 16 carries out eccentric swing rotation.Due to external gear 16 and internal gear 14 internal messing, therefore by the swing rotary of this external gear 16, there is the phenomenon that external gear 16 offsets successively with the engaging position of internal gear 14.
Thus, input shaft 18 often rotates once, and external gear 16 rotates (rotation) corresponding amount poor to the number of teeth of internal gear 14 relatively relative to the internal gear 14 being in stationary state, i.e. " 1 tooth amount ".This rotation composition is passed to the vibrating part 36 of the axial side being configured at external gear 16 via roller member 40 and pin parts 38, and the output shaft assembly 44 integrated with vibrating part 36 is rotated.Its result, can realize the deceleration of the reduction speed ratio being equivalent to (internal gear 14 is poor with the number of teeth of external gear 16: be 1 in this example)/(number of teeth of external gear 16).
Wherein, the oil sealing 72 of input shaft 18 is configured at than input shaft bearing 60 more by the position in the axially outside of this input shaft 18.Further, in order to suppress the increase of the swing resistance of eccentric body 28, the liquid level Li1 of oiling agent is set as the sealing labial surface 72B1 of the primary seal lip 72B lower than this oil sealing 72.Therefore, because oil sealing 72 is positioned at the axially outside of input shaft bearing 60, therefore, oiling agent cannot fully arrive on the sealing labial surface 72B1 of this oil sealing 72 in the past, there is problem easy to wear.
But in the present embodiment, shell 34 (cover body shell 54) has to be communicated with at the radial outside of input shaft bearing 60 and more leans on lubrication channel 78,79 between the space P1 of device private side and oil sealing 72 than this input shaft bearing 60.And the lubrication channel 78 of upside wherein has the plane of inclination 78D tilted relative to input shaft 18.
Therefore, immediately below such as, near the entrance being splashed to the lubrication channel 78 of upside by the eccentric swing of the peripheral part 28A of eccentric body 28, the oiling agent of (near the top 78D1 of plane of inclination 78D) can not directly fall to, but can descending in lubrication channel 78 along this plane of inclination 78D while walk around input shaft bearing 60 and arrive oil sealing 72 side.
Further, the end 78D2 due to this plane of inclination 78D is positioned at than back-up ring 74 more by the position of oil sealing 72 side, and oiling agent becomes the form stopped by 74 of this back-up ring thus, prevents the oil sealing opposition side (axial device private side) getting back to input shaft bearing 60.Therefore, (although being the structure of position lower than the sealing labial surface 72B1 of oil sealing 72 of the liquid level Li1 of oiling agent), the oiling agent in shell 34 can stride across input shaft bearing 60 and guide to oil sealing 72.
In other words, while the lubrication of sealing labial surface 72B1 of oil sealing 72 can be maintained well, the position of the liquid level Li1 of oiling agent is maintained the sealing labial surface 72B1 lower than oil sealing 72.Therefore, it is possible to the increase of the stirring resistance of the oiling agent suppressing the swing because of eccentric body 28 (starting of oscillation parts 30) or eccentric body bearing 32 to cause, and the enclosed volume of oiling agent can be reduced.
Further, especially in this embodiment, near the top 78D1 of lubrication channel 78, there is the eccentric body 28 of speed reducer 12.Eccentric body 28 carries out eccentric swing at such as upper/lower positions, can not impregnated in oiling agent when this eccentric body 28 is eccentric upward, and the position of dipping time eccentric downwards.Therefore, when swinging, the outer weekly assembly turnover oiling agent of eccentric body 28, can make oiling agent effectively splash near the top 78D1 of lubrication channel 78 thus at every turn.
Further, in present embodiment, as the stuffing box bearing that input shaft bearing 60 adopts the axis of rolling element 60C outside to be shielded by sealed member 60D.Therefore, the generation oiling agent next along the outside of the outer ring 60A of input shaft bearing 60 can be avoided along the end of the oil sealing side axially of this outer ring 60A to enter the phenomenon (that is, not flowing to the phenomenon of oil sealing side) of the P2 side, space having rolling element 60C.
Further, the lubrication channel 78 involved by present embodiment can be formed simply by general work mechanisms such as end mills (or casting mold can also be utilized to be formed, thus omit machining), therefore cost is lower.Further, about the back-up ring 74 that " dykes and dams " as oiling agent play a role, being the parts arranged to limit moving axially of input shaft bearing 60 originally, therefore can not causing the increase of parts number of packages, also can realize low cost in this.
The variation of above-mentioned mode of execution shown in Fig. 4.
In speed reducer 12 (whirligig) involved by this variation, except the axle sleeve 80 of mode of execution before, also have be embedded in input shaft 18 sweep blade (gomphosis part) 90.
This sweeps blade 90 and is made up of ring-shaped member, and it possesses peripheral part 92, and described peripheral part 29 has external diameter (radius) r90 of the distance L of axle center C18 to the liquid level Li1 of oiling agent (C18-Li1) be greater than from input shaft 18.That is, the part sweeping blade 90 is submerged in oiling agent.Further, this sweeps in blade 90, and described peripheral part 92 is from the private side side direction surface thereof (external diameter r90 becomes large gradually) towards the outside of speed reducer 12.
Other structures are identical with mode of execution before, therefore give identical symbol to identical or functionally similar position in the drawings, and omit repeat specification.
According to this mode of execution, when sweeping blade 90 and together rotating with input shaft 18, oiling agent is together swept with the rotation sweeping blade 90, and along peripheral part 92 acclivity and swept near the top 78D1 of lubrication channel 78.Therefore, it is possible to realize aforesaid effect more well, and oil sealing 72 side of can more effectively oiling agent being led.
In addition, in the present invention, sweeping blade might not be necessary parts, also can not sweep blade.Further, when setting sweeps blade, shape is also not limited to above-mentioned shape, such as, be somely concavo-convexly set to the shape of more easily scraping super fatting agent by arranging on surface.
Further, in this mode of execution, be configured with special (parts separated with input shaft) gomphosis part as sweeping blade, but gomphosis part might not be the parts separated with input shaft.That is, can be the parts integrated with input shaft.Or, also can by the parts substitute except input shaft for sweeping blade.As has been described, for mode of execution before, if change view, then can be interpreted as and make starting of oscillation parts (or eccentric body) itself as the example having this gomphosis part sweeping function and play a role.
Further, from this viewpoint, such as, can be configured to, the axial width of eccentric body is formed as larger (starting point closer to the plane of inclination of lubrication channel) by (better sweeping function to have).And, in eccentric oscillating-type speed reducer, it is also known that only have the device of 1 external gear, but now, in order to obtain the transient equiliblium of swing rotary, be usually arranged on the balancer weight direction contrary with the eccentric direction of eccentric body with center of gravity.Now, this balancer weight can be made to play a role as " having the gomphosis part sweeping function ".Balancer weight is structurally easily designed to together pass in and out oiling agent with the rotation of input shaft, therefore, it is possible to make it play a role well as " having the gomphosis part sweeping function ".
Further, in the above-described embodiment, have employed the stuffing box bearing being configured with sealed member in oil sealing side as input shaft bearing, and be configured to avoid the oiling agent next along lubrication channel to enter along the outer ring of input shaft bearing the side, space having rolling element.But, the structure that this structure is also not necessarily necessary.Such as, in the structure of whirligig, when can expect oiling agent by flowing to the effect of oil sealing side between the outer ring of bearing and inner ring, the bearing that there is not sealed member can be adopted as bearing.
In addition, in the above-described embodiment, the present invention is applicable to eccentric oscillating-type speed reducer, but the present invention's whirligig applicatory is not limited to this speed reducer, the whirligig comprising various speeder or gearing can be applicable to.
Further, in above-mentioned mode of execution, the present invention is applicable to the lubrication of the oil sealing of input shaft.The present invention is when being applicable to the lubrication of the rotating speed oil sealing of input shaft faster, and can obtain significant action effect, but " axle " involved in the present invention being not limited to input shaft, such as, also can be output shaft.
Claims (5)
1. a whirligig, it possesses: the shell being sealed with oiling agent, the axle running through this shell, the bearing being configured at the described axle between this axle and shell and oil sealing, and the feature of described whirligig is,
Described oil sealing is configured at than described bearing more by the axially outside of described axle,
Moving axially of described bearing is limited by back-up ring, and described back-up ring is more leaning on the private side of described whirligig to be embedded in the circlip groove of described shell than described bearing,
Described shell has lubrication channel at the radial outside of described bearing, between the space that this lubrication channel is communicated with the private side more leaning on described whirligig than this bearing and described oil sealing,
This lubrication channel has the plane of inclination tilted relative to described axle,
The end of this plane of inclination is presented axially in than described back-up ring more by described oil sealing side.
2. whirligig according to claim 1, is characterized in that,
The liquid level of described oiling agent is lower than the sealing labial surface of described oil sealing.
3. whirligig according to claim 1 and 2, is characterized in that,
Described whirligig has the gomphosis part being embedded in described axle,
This gomphosis part has peripheral part, and the external diameter of described peripheral part is greater than the distance of axle center to the liquid level of described oiling agent from described axle.
4. whirligig according to claim 3, is characterized in that,
Described whirligig is possess the eccentric oscillating-type speed reducer as lower component: internal gear; External gear, with this internal gear internal messing while swing; And described axle, there is the eccentric body for making this external gear swing,
Described gomphosis part is the described eccentric body of this eccentric oscillating-type speed reducer.
5. the whirligig according to claim 3 or 4, is characterized in that,
Described gomphosis part is made up of ring-shaped member, and outer circumferential face is from the private side side direction surface thereof towards the outside of described whirligig.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014060986A JP6182487B2 (en) | 2014-03-24 | 2014-03-24 | Rotating device |
| JP2014-060986 | 2014-03-24 |
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| Publication Number | Publication Date |
|---|---|
| CN104948720A true CN104948720A (en) | 2015-09-30 |
| CN104948720B CN104948720B (en) | 2018-05-01 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201510039594.1A Active CN104948720B (en) | 2014-03-24 | 2015-01-26 | Rotating device |
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| Country | Link |
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| JP (1) | JP6182487B2 (en) |
| KR (1) | KR101681249B1 (en) |
| CN (1) | CN104948720B (en) |
Cited By (2)
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| CN107269817A (en) * | 2016-03-31 | 2017-10-20 | 住友重机械工业株式会社 | Rotating device |
| CN113374858A (en) * | 2021-07-15 | 2021-09-10 | 中信重工机械股份有限公司 | Gear pair for grinding machine |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP6723657B2 (en) | 2016-12-05 | 2020-07-15 | 住友重機械工業株式会社 | Reducer |
| JP6730680B2 (en) * | 2016-12-27 | 2020-07-29 | 三菱自動車エンジニアリング株式会社 | Drive machine case |
| JP6811634B2 (en) | 2017-02-10 | 2021-01-13 | 住友重機械工業株式会社 | Planetary gear device |
| JP6767290B2 (en) * | 2017-03-10 | 2020-10-14 | 住友重機械工業株式会社 | Planetary gear device |
| CN107620793B (en) * | 2017-09-19 | 2024-01-12 | 中国第一汽车股份有限公司 | Through shaft unit structure |
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Also Published As
| Publication number | Publication date |
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| KR101681249B1 (en) | 2016-11-30 |
| JP6182487B2 (en) | 2017-08-16 |
| CN104948720B (en) | 2018-05-01 |
| KR20150110304A (en) | 2015-10-02 |
| JP2015183780A (en) | 2015-10-22 |
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