CN102011858B - Planetary reducer - Google Patents
Planetary reducer Download PDFInfo
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- CN102011858B CN102011858B CN201010270741.3A CN201010270741A CN102011858B CN 102011858 B CN102011858 B CN 102011858B CN 201010270741 A CN201010270741 A CN 201010270741A CN 102011858 B CN102011858 B CN 102011858B
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- shell
- main bearing
- internal gear
- planetary reducer
- 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
Abstract
The present invention provides a planetary reducer which can prevent size enlargement of the planetary reducer and is not provided with a main bearing with a large diameter. The planetary reducer is provided with the following components: a tapered roller bearing (128) which rotatably supports a gear carrier (120); a housing (136) which is provided with an inner diameter (D1) part that is smaller than an outer diameter (d1) of an outer ring (128C) of the tapered roller bearing (128) between the object machines (150), wherein, the housing (136) is divided into an output side housing (138) and an input side housing (137). The tapered roller bearing (128) is configured more next to the object machine in an axial direction (O). The input side housing (137) comprises an inner gear (134) with integrally formed profile parts. Furthermore the output side housing (138) is connected with the input side housing (137).
Description
Technical field
The application advocates the preference of No. 2009-203606th, the Japanese patent application based on application on September 3rd, 2009.The full content of this application is by referring to being applied in this specification.
The present invention relates to a kind of planetary reducer.
Background technique
In the planetary reducer shown in patent documentation 1, internal gear and shell become Split type structure.Therefore, can expect as follows: in the planetary reducer shown in patent documentation 1, also can not make to change with the link form of object machinery even if this shell has the inner-diameter portion whose less than the outer ring external diameter of rotatably this main bearing of support roller support body between main bearing and object machinery and make planetary reducer high capacity.At this, in patent documentation 1, be pressed into ejector pin and at shell fixed annulus vertically.
Patent documentation 1:WO99/25992 publication
But, in the structure shown in patent documentation 1, configure main bearing at the radial direction of wheel support body more in the inner part than the position of press-in ejector pin.That is, in the planetary reducer shown in patent documentation 1, for guaranteeing the space being pressed into ejector pin, the internal diameter of the housing parts that supporting spindle holds must be reduced.For this reason, must make the reduced of main bearing, therefore cause the capacity of main bearing to diminish, Driving Torque or torque rigidity also diminish.In addition, when strengthening the diameter of main bearing, planetary reducer itself will be caused to maximize.
Summary of the invention
Therefore, the present invention is for solving the problem a little and completing, its problem is, a kind of planetary reducer is provided, retarder itself also can not be made to maximize even if this planetary reducer shell has the inner-diameter portion whose less than the outer ring external diameter of rotatably this main bearing of support roller support body between main bearing and object machinery and large diameter main bearing is set.
The present invention solves described problem by following structure: a kind of planetary reducer, possesses planetary pinion, the internal gear of this planetary pinion institute internal messing, the wheel support body synchronous with described planetary revolution composition or rotation composition, rotatably support the main bearing that this takes turns support body, there is the shell of the inner-diameter portion whose less than the outer ring external diameter of this main bearing between this main bearing and object machinery, wherein, described shell is formed in object mechanical side and the split of object machinery opposition side, more described main bearing is configured by described object mechanical side in the axial direction than described internal gear, described internal gear is integrally formed with comprising the toothed region of internal gear at the shell of described object machinery opposition side, and the shell of the shell of described object mechanical side and described object machinery opposition side is connected.
Shell is divided into split in object mechanical side and object machinery opposition side by the present invention, is integrally formed internal gear with comprising toothed region at the shell of object machinery opposition side.Therefore, even if the shell of object mechanical side has the inner-diameter portion whose less than the outer ring external diameter of this main bearing between main bearing and object machinery, also this main bearing (from object machinery opposition side) can be assembled in the shell of object mechanical side.
And, be set to and shell is divided into split in object mechanical side and object machinery opposition side, comprise toothed region at the shell of object machinery opposition side and be integrally formed internal gear, and then the structure of the shell of the shell of object of connection mechanical side and object machinery opposition side, therefore, it is possible to planetary reducer itself is not made to maximize and configure large diameter main bearing.Thus, can strengthen the capacity of main bearing, result can make Driving Torque or torque rigidity improve.
Namely, when as prior art internal gear and shell being set to Split type structure, or when internal gear and shell are set to integrative-structure and internal gear and its toothed region are set to Split type structure, in order to internal gear or toothed region are fixed on shell, also the internal diameter of the part of the main bearing of the part, the i.e. supporting shell that adjoin with internal gear or the toothed region of shell vertically must be reduced, result exists or reduces the diameter of main bearing, if or do not reduce the diameter of main bearing, then retarder itself is by the problem maximized.
In contrast, the present invention, by having said structure, without the need to reducing the internal diameter of the part adjoined with the internal gear of shell vertically, therefore can not make retarder itself maximize and configure large diameter main bearing.Its result, can strengthen the capacity of main bearing and Driving Torque and torque rigidity can be made to improve.
Invention effect
According to the present invention, planetary reducer itself can not be made to maximize and adopt large diameter main bearing, therefore can strengthen the capacity of main bearing and Driving Torque and torque rigidity can be made to improve.
Accompanying drawing explanation
Fig. 1 is the cross-sectional schematic of an example of the major component of the planetary reducer represented involved by the 1st mode of execution of the present invention.
Fig. 2 be represent planetary reducer involved by the 1st mode of execution of the present invention, cross-sectional schematic when linking shell and input side shell.
Fig. 3 is the cross-sectional schematic of an example of the major component of the planetary reducer represented involved by the 2nd mode of execution of the present invention.
In figure: 100, 200-planetary reducer, 114, 214-planetary pinion, 116, 216-needle roller, 118, 218-planet pin, 120, 220-takes turns support body, 121, 221-takes turns support body plate, 122, 222-wheel carrier phosphor bodies, 126, 128, 226, 228-tapered roller bearing, 126A, 128A-inner ring, 126B, 128B-tapered roller, 126C, 128C-outer ring, 130, 230-output shaft, 134, 234-internal gear, 134A-toothed region (internal tooth), 136, 236-shell, 137, 237-input side shell, 138, 238-outlet side shell, 150, 250-object machinery, 152, 252-connected with outer casing.
Embodiment
Below, be described in detail with reference to the example of accompanying drawing to embodiments of the present invention.
Fig. 1 is the sectional view of the major component of the planetary reducer involved by an example representing the 1st mode of execution of the present invention.
Planetary reducer 100 is simple planetary mechanism, has not shown sun gear, planetary pinion 114, wheel support body 120 and internal gear 134 at shell 136.In addition, shell 136 is divided into the input side shell 137 as the outlet side shell 138 of the shell of the object mechanical side being connected to planetary reducer 100 and the shell as object machinery opposition side.
Such as be provided with helical gear (also can be spur wheel) at sun gear, be meshed with planetary pinion 114.Sun gear is such as linked to the motor drive shaft of not shown motor by the coupling shaft of not shown cylindrical shape.
Planetary pinion 114 is configured with multiple in the periphery of sun gear, and revolves round the sun while rotation around sun gear.Planetary pinion 114 is supported on planet pin 118 by needle roller 116.Needle roller 116 configures with total roller state, and axial O is divided into 2.Therefore, when sun gear is meshed with internal gear 134 with planetary pinion 114, planetary pinion 114, the end thereof contacts of needle roller 116 can be reduced, and, under without total roller state of retainer, use needle roller 116, therefore can by larger transmission of torque to planet pin 118.In addition, between 2 needle rollers 116, annular liner 116A is configured with.And between the inner circumferential and the periphery of planet pin 118 of liner 116A, be provided with clearance G and become the structure keeping oiling agent (lubricating grease) in clearance G.Therefore, even if planetary pinion 114 rotates also lubricating grease stably can be supplied to needle roller 116.Now, the gap as kept lubricating grease also can be set between the periphery of liner 116A and the inner circumferential of planetary pinion 114.Now, by the revolution of planetary pinion 114, the center of liner 116A relative to the center eccentric motion of planet pin 118, so the lubricating grease of the periphery of liner 116A and inner circumferential can be supplied to needle roller 116 effectively.That is, planetary pinion 114 long lifetime can be made.
In addition, be configured with at the two ends of the axial O of needle roller 116 for preventing needle roller 116 to emerge to axial O and preventing the stop component 116B of needle roller 116 and the wearing and tearing of wheel support body 120.
Planet pin 118 is supported on the wheel support body 120 wheel support body plate 121 and wheel carrier phosphor bodies 122 linked.Wheel carrier phosphor bodies 122 is concluded by bolt 124 or is fixed on wheel support body plate 121.Therefore, take turns support body 120 synchronous with the revolution composition of planetary pinion 114 and take out this by planet pin 118 and revolve round the sun into and assign to rotate.The output shaft 130 of flange shape is wholely set at the planetary pinion opposition side of wheel carrier phosphor bodies 122.This end face 130A is provided with multiple bolt hole 132, links not shown bolt at this bolt hole 132, be thus connected the driven shaft of object machinery 150.Tapered roller bearing 126 (supplementary bearing), 128 (main bearings) are configured at periphery 121A, 122A of wheel support body plate 121 and wheel carrier phosphor bodies 122, thus rotatably support roller support body plate 121 and wheel carrier phosphor bodies 122.That is, as shown in Figure 1, on the radial direction of wheel support body 120, tapered roller bearing 126,128 is configured with in the outside of planet pin 118.
The outlet side shell 138 in shell 136 is configured with in the outside of the outer ring 128C of tapered roller bearing 128.In outlet side shell 138, on axial O, between the position of tapered roller bearing 128 and be connected object machinery 150, be formed with internal diameter D1 part (D1 < d1) less than the outer ring 128C outside diameter d 1 of tapered roller bearing 128.This magnitude relationship is based on following formation: the periphery 138A of outlet side shell 138 is coincide with the inner circumferential 152A of the connected with outer casing 152 of object machinery 150 and as chimeric with the inner circumferential 152A of connected with outer casing 152 and install time become benchmark recess portion (Yin ?portion) E1 plays a role.Therefore, the axle center of outlet side shell 138 can be made consistent accurately on axial O with the axle center of object machinery 150 by recess portion E1.Further, abutted with the end face 138C of the flange part 138B of outlet side shell 138 by the end face 152C of the connected with outer casing 152 of object machinery 150, axial O carries out the location of the connected with outer casing 152 on the periphery 138A of outlet side shell 138.Further, in outlet side shell 138, tapered roller bearing 128 is configured at by axial O the outside (be right side in Fig. 1, or be object machinery opposition side) of recess portion E1.Therefore, even if strengthen the heavy wall that tapered roller bearing 128 also fully can thicken the part 138E of outlet side shell 138 outside tapered roller bearing 128.That is, outlet side shell 138 can form the high outer rigid housing can allowing the large torque putting on tapered roller bearing 128.
On the other hand, the input side shell 137 in shell 136 is configured with in the outside of the outer ring 126C of tapered roller bearing 126.The internal gear 134 with planetary pinion 114 internal messing is integrally formed with comprising its toothed region (internal tooth) 134A at input side shell 137.And, in input side shell 137, the axial O both sides (to avoid the mode with the interference of the retainer keeping tapered roller 126B, 128B) of internal gear 134 are provided with teat 134B, 134C of abutting with (outside) outer ring 126C, 128C of tapered roller bearing 126,128.At this, at outer ring 126C, 128C of the axial O both sides configuration tapered roller bearing 126,128 of the internal gear 134 of input side shell 137.For this reason, axial O gets tapered roller bearing 126, teat 134B, internal gear 134, teat 134C, tapered roller bearing 128 form side by side.In addition, tapered roller bearing 126,128 is configured with in back-to-back double-linked combination mode.Therefore, high radial load and axial load can be supported.
Input side shell 137 and outlet side shell 138 are linked by bolt 140 on axial O.As shown in Figure 1, this linking portion C is arranged at the periphery 137A of (from position A to position B) within the scope of the axial O existing for internal gear 134 of input side shell 137.At this, because the inner circumferential 138D becoming outlet side shell 138 covers the form of the periphery 137A of input side shell 137, therefore the form part of the arrival linking portion C of the periphery 137A of input side shell 137 plays a role as the recess portion E2 of outlet side shell 138 with input side shell 137.Therefore, O can realize the link of input side shell 137 and outlet side shell 138 shortlyer vertically, the axle center of input side shell 137 can be made consistent accurately on axial O with the axle center of outlet side shell 138 simultaneously.
In addition, the toothed region 134A of internal gear 134 is positioned near the end of input side shell 137.Therefore, during processing toothed region 134A, the cutter arbor support carrying out cog machining can be made closer to being cut portion (toothed region 134A), and can warpage etc. be prevented.Thus, can the toothed region 134A of precision machining interal 134 well.
In addition, the oil sealing of mark 142 for being configured between outlet side shell 138 and wheel carrier phosphor bodies 122 inside and outside sealed planetary retarder 100 of Fig. 1.
Then, Fig. 1, Fig. 2 assemble sequence to planetary reducer 100 is utilized to be described.
First, make the inner ring 128A of tapered roller bearing 128 and tapered roller 128B be configured at the periphery 122A of wheel carrier phosphor bodies 122, and make wheel carrier phosphor bodies 122 be configured at the inner side of outlet side shell 138 from object machinery opposition side.
Then, as shown in Figure 2, by the outer ring 128C of tapered roller bearing 128 vertically O be configured at the inner circumferential 138D of outlet side shell 138 movably.And, on axial O by the teat 134C of internal gear 134 from object machinery opposition side to while object mechanical side is pressed into outer ring 128C, input side shell 137 is assembled in outlet side shell 138, is made it to link and fixing outer ring 128C and input side shell 137 by bolt 140.And, at the periphery 137A of input side shell 137, under axial O is connected to the state of teat 134B of internal gear 134, the outer ring 126C of configuration tapered roller bearing 126.In addition, in fig. 2, be configured with oil sealing 142, but also can have configured afterwards as described later.
Then, make planet pin 118 be configured at the precalculated position of wheel carrier phosphor bodies 122, and make needle roller 116, liner 116A, stop component 116B, planetary pinion 114 be embedded in this planet pin 118.And, by bolt 124, wheel carrier phosphor bodies 122 and wheel support body plate 121 are installed.During installation, configure inner ring 126A and the tapered roller 126B of tapered roller bearing 126 at the periphery 121A of wheel support body plate 121.In addition, oil sealing 142 is made to be configured between output shaft 130 and outlet side shell 138.Now, pad (not shown) inserts by axial O between object machinery opposition side (being right side in FIG) of inner ring 126A and the shoulders 121B of wheel support body plate 121, easily can adjust the pressurization of tapered roller bearing 126,128 thus.In addition, the position of inserting pad is not limited to this position, as long as the position of the pressurization of adjustable tapered roller bearing 126,128 can be then random position.
Then, make press-in be configured at the inner side of planetary pinion 114 in the sun gear of not shown coupling shaft, be bolted input side shell 137 with bolt hole 142 and rotatably support the case member of this sun gear, planetary reducer 100 can be assembled thus.That is, only can from the object of axial O machinery opposition side assembling planetary reducer 100, therefore easily carry out assembling and repair, part replacement.And, during assembling, can pressurization of (pad etc. by not shown) simple adjustment tapered roller bearing 126,128, therefore eliminate wheel support body 120 and can maintain high-precision rotation relative to the loosening etc. of input side shell 137 and outlet side shell 138.Further, therefore also torque rigidity can be improved.
Then, the effect of planetary reducer 100 is described.
Sun gear is such as rotated by coupling shaft according to the rotation of not shown motor.Like this, internal gear 134 is in stationary state, and therefore the revolution composition trailing wheel support body 120 of planetary pinion 114 takes out.Wheel support body 120 makes the driven shaft of the object machinery 150 be installed on output shaft 130 rotate.
In present embodiment, shell 136 split is divided into the outlet side shell 138 of object mechanical side and the input side shell 137 of object machinery opposition side, is integrally formed internal gear 134 with comprising toothed region 134A at input side shell 137.Therefore, even if outlet side shell 138 has the internal diameter D1 part less than the outer ring outside diameter d 1 of this tapered roller bearing 128 as main bearing between tapered roller bearing 128 and object machinery, also this tapered roller bearing 128 (from object machinery opposition side) can be installed on outlet side shell 138.
And, owing to being set to following structure, outlet side shell 138 and input side shell 137 is divided into by shell 136 split, internal gear 134 is integrally formed with comprising toothed region at input side shell 137, and then link outlet side shell 138 and input side shell 137, therefore can configure large diameter tapered roller bearing 128 without the need to making planetary reducer 100 itself maximize.Thus, can strengthen the capacity of tapered roller bearing 128, result can make Driving Torque or torque rigidity improve.
Namely, when as prior art internal gear and shell being set to Split type structure, or when internal gear and its toothed region being set to Split type structure internal gear and shell being set to integrative-structure, in order to internal gear or toothed region are fixed on shell, the internal diameter of the part of the main bearing of part, the i.e. supporting shell that also the internal gear of O and shell vertically or toothed region must be adjoined reduces, result exists or reduces the diameter of main bearing, if or do not reduce the diameter of main bearing, then the problem of planetary reducer maximization itself.
In contrast, present embodiment is by having said structure, without the need to the internal diameter D1 of the part that the internal gear 134 reducing O and shell 136 vertically adjoins, therefore without the need to making planetary reducer 100 itself maximize, large diameter tapered roller bearing 128 can be configured as main bearing.Its result, can strengthen the capacity of main bearing, and Driving Torque and torque rigidity can be made to improve.
And, input side shell 137 and the linking portion C of outlet side shell 138 are arranged at the periphery 137A of the axial O scope existing for internal gear 134 of input side shell 137, therefore, it is possible to make the form part of the periphery 137A of the input side shell 137 of this linking portion of arrival C play a role as the recess portion E2 of outlet side shell 138 with input side shell 137.For this reason, the axle center that input side shell 137 and outlet side shell 138 can be made respective is consistent accurately with axial O, and therefore planetary reducer 100 can realize the rotation smoothly of shaftless swing for a long time.Meanwhile, can be shorter on axial O realize the link of input side shell 137 and outlet side shell 138, the axial length of planetary reducer 100 can be shortened.
Further, the periphery 138A of outlet side shell 138 as the inner circumferential 152A of the connected with outer casing 152 with object machinery 150 chimeric and install time become benchmark recess portion E1 play a role, therefore easily carry out object machinery 150 and planetary reducer 100 to axle.
Further, tapered roller bearing 128 is configured at outside the radial direction than planet pin 118 more roller support body 120, therefore can strengthen tapered roller bearing 128 further.Therefore, it is possible to increase the capacity of the radial load putting on wheel support body 120 further.
Further, possess the tapered roller bearing 126 as supplementary bearing, the wheel support body plate 121 forming wheel support body 120 is supported on the opposition side of tapered roller bearing 128 by this tapered roller bearing on axial O relative to internal gear 134, therefore can be set to larger Driving Torque.Meanwhile, the axle center of wheel support body 120 can be made consistent accurately with axial O, therefore successfully can keep the rotation taking turns support body 120.And, use tapered roller bearing 126,128 in back-to-back double-linked combination mode, therefore, it is possible to support high radial load and axial load.
Further, in the present embodiment, take turns support body 120 to become link and be supported on the wheel support body plate 121 of tapered roller bearing 126,128 and the structure of wheel carrier phosphor bodies 122 respectively.And inner ring 126A, 128A of tapered roller bearing 126,128 are configured at the periphery 121A of wheel support body plate 121, the periphery 122A of wheel carrier phosphor bodies 122 respectively.The outer ring 128C of tapered roller bearing 128 is configured at the inner circumferential 138D of outlet side shell 138, to make to be fixed on axial O when linking outlet side shell 138 and input side shell 137.Further, the outer ring 126C of tapered roller bearing 126 is configured at the periphery 137A of input side shell 137.Therefore, when linking wheel support body plate 121 and wheel carrier phosphor bodies 122, on axial O, between the object machinery opposition side (being right side in FIG) and the shoulders 121B of wheel support body plate 121 of the inner ring 126A of tapered roller bearing 126, insert pad etc., easily can adjust the pressurization of tapered roller bearing 126,128 thus.Therefore, wheel support body 120 can be eliminated and maintain high-precision rotation relative to loosening of shell 136.Further, therefore also torque rigidity can be improved.
Thus, according to the present embodiment, large diameter tapered roller bearing 128 can be adopted without the need to making planetary reducer 100 itself maximize, so the capacity of the tapered roller bearing 128 of wonderful works main bearing can be added, Driving Torque and torque rigidity can be made to improve.
Lift the 1st mode of execution to describe the present invention, but the invention is not restricted to the 1st mode of execution.That is, the change that can not depart from improvement in the scope of present inventive concept and design is self-evident.
Such as, in the 1st mode of execution, output shaft 130 is flange shape, but the present invention is not limited thereto, and is easy to the shape changing output shaft according to the shape of the driven shaft of object machinery.Such as, as shown in the 2nd mode of execution of Fig. 3, also columniform output shaft 230 can be set at wheel carrier phosphor bodies 222, be connected with the driven shaft of object machinery 250 by keyway 230A.In addition, this kind of what is called is easily carried out by means of only the change of the parts (take turns support body and output shaft, or output shaft being additional) forming output shaft the change (the 1st mode of execution is called flange type) of solid type output shaft with can not damaging action effect of the present invention.That is, commonization of the parts formed outside output shaft can be sought, therefore, it is possible to seek the cost degradation of the planetary reducer of the output shaft possessing flange type or solid type.
Further, in the above-described embodiment, set casing and arrange output shaft at wheel support body, but the present invention may not be defined in this, also can be fast pulley support body and rotational shell and obtain output, so-called frame rotation type.
Further, in the above-described embodiment, employ 2 tapered roller bearings, but the present invention may not be defined in this in back-to-back double-linked combination mode, also can be the situation of use 1 bearing.Such as can only use at the position of the tapered roller bearing (main bearing) 128 of Fig. 1 configuration crossed roller bearing.Now, also can in the axial load axially bearing twocouese of the driven shaft of object machinery, and the action effect identical with when using 2 tapered roller bearings can be obtained, and then the shortening of planetary reducer O vertically can be realized.
Further, when using 2 bearings, not only can use tapered roller bearing, also can use angular contact bearing (roller or ball), its combination is also not limited to back-to-back duplex, also can be face-to-face double-linked combination or back to face double-linked combination.
Further, in the above-described embodiment, planetary reducer is simple planetary mechanism, but the present invention may not be defined in this.Such as planetary pinion can be the external gear being carried out swing rotary by the rotation of eccentric body.Now, planet pin (wheel carrier pin) is synchronous with the rotation composition of external gear, takes out the rotation composition of external gear from this planet pin.Certainly, the frame rotation type that shell rotates can be now also set to.
Claims (5)
1. a planetary reducer, possess planetary pinion, the internal gear of this planetary pinion institute internal messing, the wheel support body synchronous with described planetary revolution composition or rotation composition, rotatably support this main bearing of taking turns support body and there is the shell of the inner-diameter portion whose less than the outer ring external diameter of this main bearing between this main bearing and object machinery, it is characterized in that
Described shell is formed in object mechanical side and the split of object machinery opposition side,
Described main bearing is configured at the shell of described object mechanical side in the axial direction with more leaning on described object mechanical side than described internal gear,
Described internal gear is integrally formed with comprising the toothed region of internal gear at the shell of described object machinery opposition side, and,
The shell of the shell of described object mechanical side and described object machinery opposition side is connected,
The shell of described object machinery opposition side has the teat abutted against with the outer ring of described main bearing,
The linking portion of shell of the shell of described object mechanical side and described object machinery opposition side is arranged at the periphery of shell in the axial range existing for described internal gear of this object machinery opposition side.
2. planetary reducer as claimed in claim 1, is characterized in that,
Chimeric and the recess portion becoming benchmark when installing plays a role as the inner circumferential of the connected with outer casing with described object machinery for the periphery of the shell of described object mechanical side.
3. planetary reducer as claimed in claim 1 or 2, is characterized in that,
Described planetary pinion is supported by planet pin,
Described main bearing is configured at than this planet pin more by outside described radial direction of taking turns support body.
4. the planetary reducer as described in any one in claims 1 to 3, is characterized in that,
Also possess supplementary bearing, described supplementary bearing, axially described, takes turns described support body to be supported on described main bearing opposition side relative to described internal gear.
5. planetary reducer as claimed in claim 4, is characterized in that,
Described main bearing and supplementary bearing are respectively tapered roller bearing, and use in back-to-back double-linked combination mode.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009203606A JP5528744B2 (en) | 2009-09-03 | 2009-09-03 | Planetary reducer |
| JP203606/2009 | 2009-09-03 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102011858A CN102011858A (en) | 2011-04-13 |
| CN102011858B true CN102011858B (en) | 2015-07-01 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201010270741.3A Active CN102011858B (en) | 2009-09-03 | 2010-09-01 | Planetary reducer |
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| Country | Link |
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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 |
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| 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 |
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- 2010-08-16 KR KR1020100078654A patent/KR101248388B1/en active IP Right Grant
- 2010-09-01 DE DE102010036063.5A patent/DE102010036063B4/en active Active
- 2010-09-01 CN CN201010270741.3A patent/CN102011858B/en active Active
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| US4091688A (en) * | 1976-09-01 | 1978-05-30 | Dana Corporation | Easily assembled and disassembled planetary gear assembly |
| CN1478183A (en) * | 2000-12-22 | 2004-02-25 | ������˹�۳��ֹ����ɷݹ�˾ | Planetary gear device |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102011858A (en) | 2011-04-13 |
| KR101248388B1 (en) | 2013-03-28 |
| DE102010036063A1 (en) | 2011-04-07 |
| JP2011052785A (en) | 2011-03-17 |
| JP5528744B2 (en) | 2014-06-25 |
| KR20110025079A (en) | 2011-03-09 |
| TW201109548A (en) | 2011-03-16 |
| TWI404872B (en) | 2013-08-11 |
| DE102010036063B4 (en) | 2020-12-17 |
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