CN203335738U - Power transmission device - Google Patents
Power transmission device Download PDFInfo
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- CN203335738U CN203335738U CN2013203044553U CN201320304455U CN203335738U CN 203335738 U CN203335738 U CN 203335738U CN 2013203044553 U CN2013203044553 U CN 2013203044553U CN 201320304455 U CN201320304455 U CN 201320304455U CN 203335738 U CN203335738 U CN 203335738U
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- 230000005540 biological transmission Effects 0.000 title abstract description 5
- 230000015572 biosynthetic process Effects 0.000 description 5
- 238000005755 formation reaction Methods 0.000 description 5
- 230000014509 gene expression Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 3
- 239000003638 chemical reducing agent Substances 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 206010044565 Tremor Diseases 0.000 description 1
- 230000010485 coping Effects 0.000 description 1
- 230000005520 electrodynamics Effects 0.000 description 1
- ZZUFCTLCJUWOSV-UHFFFAOYSA-N furosemide Chemical compound C1=C(Cl)C(S(=O)(=O)N)=CC(C(O)=O)=C1NCC1=CC=CO1 ZZUFCTLCJUWOSV-UHFFFAOYSA-N 0.000 description 1
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Abstract
The utility model provides a power transmission device which comprises a planetary gear mechanism (7) formed by a sun gear (5a), a gear ring (28) and a plurality of planetary gears (21 and 22) arranged between the sun gear (5a) and the gear ring (28). The planetary gears are provided with first ends on one side, in the axial direction (J), of the sun gear (5a) and second ends on the other side, in the axial direction (J), of the sun gear (5a). The planetary gears comprise first planetary gears (21) and second planetary gears (22), wherein the lateral portion of the first end of each gear tooth (34) of each first planetary gear (21) is a convex portion (35), the lateral portion of the second end of each gear tooth (34) of each first planetary gear (21) is a concave portion (36), the lateral portion of the first end of each gear tooth (34) of each second planetary gear (22) is a concave portion (36), and the lateral portion of the second end of each gear tooth (34) of each second planetary gear (22) is a convex portion (36). Therefore, the first planetary gears (21) and the second planetary gears (22) are alternately arranged around the sun gear (5a) in the mode that the convex portions (35) of the gear teeth (34) of the first planetary gears (21) are adjacent to the concave portions (36) of the gear teeth (34) of the second planetary gears (22) or the convex portions (35) of the gear teeth (34) of the second planetary gears (21) are adjacent to the concave portions (36) of the gear teeth (34) of the first planetary gears (22).
Description
Technical field
The utility model relate to possess there is sun gear, the power transmitting deice of the planetary gears of planetary pinion, gear ring, especially, relate to the structure of the above-mentioned planetary gears for alleviating above-mentioned planetary burden.
Background technique
In the past, following such technology was known (for example,, with reference to TOHKEMY 2000-297850 communique).That is,, in the power transmitting deice carried on the moving vehicles such as the farm machinery such as combine-harvester, motorcycle, as speeder or speed reducer, carry planetary gears.In this planetary gears, be arranged on periphery configuration a plurality of (for example 3) planetary pinion and its engagement of central sun gear, and then, make interior week and this planetary periphery engagement of gear ring, be used as input side, other a Constitution Elements is used as to outlet side is at random combined by the Constitution Elements in these sun gears, planetary pinion, gear ring, thus the function of performance speeder or speed reducer.
And, for such planetary gears, from improving the viewpoint of operating efficiency, rideability etc., for above-mentioned Constitution Elements, especially, for being sandwiched in the planetary pinion that is subject to large load between sun gear and gear ring from the two, wish to improve its reliability, to this, can consider to be used planetary number (for example, from the past 3, being increased to 4) to alleviate the coping style of the load that each planetary pinion is subject to by increase.
Yet, just increase planetary number, because the planetary interval with adjacent other narrows down and mutually interferes, therefore, there is the problem that itself becomes difficult be configured.On the other hand, the internal diameter of gear ring is constant, although can be by adding the external diameter of large sun gear, reduce planetary external diameter and increase number, but exist this planetary number of teeth to tail off, contact-ratio reduces, noise during transmission of power, vibration, strength decreased, the unstable (Japanese: rotation む ら) such problem of generation rotation.
The model utility content
The power transmitting deice that the utility model relates to, form as follows in order to solve above-mentioned the problems of the prior art.
That is the power transmitting deice 1 that, the utility model relates to possesses by sun gear 5a, gear ring 28, is configured in the planetary gears 7 that a plurality of planetary pinions 21,22 between this sun gear 5a and this gear ring 28 form.The plurality of planetary pinion 21,22, a side on the axial J of this sun gear 5a has first end respectively, the opposite side on the axial J of this sun gear 5a has the second end, the plurality of planetary pinion 21,22 comprises the first planetary pinion 21 and the second planetary pinion 22, this first distolateral part of the wheel tooth 34 of this first planetary pinion 21 is that protrusion 35, this second distolateral part are concavity section 36, and this first distolateral part of the wheel tooth 34 of this second planetary pinion 22 is that concavity section 36, this second distolateral part are protrusion 35.This first planetary pinion 21 and this second planetary pinion 22 be alternate configurations around above-mentioned sun gear 5a, thereby makes the protrusion 35 of wheel tooth 34 of the side in this first, second planetary pinion 21,22 adjacent with the concavity section 36 of the opposing party's wheel tooth 34.
The above-mentioned protrusion 35 of above-mentioned first, second planetary pinion 21,22 wheel tooth 34 separately and above-mentioned concavity section 36, there is flank of tooth 35a, the 36a continuous to above-mentioned the second end from above-mentioned first end, by the middle part the above-mentioned axial J from each wheel tooth 34, to any one party in above-mentioned first, second end, make this wheel tooth 34 form vacancy, form the part with short tooth depth 36b, and it is used as to above-mentioned concavity section 36, this wheel tooth 34 remaining, part with long tooth depth 35b is used as above-mentioned protrusion 35.
Above-mentioned protrusion 35 and above-mentioned concavity section 36, respectively with total length and above-mentioned sun gear 5a and 28 engagements of above-mentioned gear ring of facewidth 35c separately, 36c on above-mentioned axial J.
Above-mentioned first, second planetary pinion 21,22 is constituted as, during along above-mentioned axial J upset, just suitable with the opposing party as a side wherein.
The power transmitting deice of the present utility model 1 formed as described above can be brought into play following effect.
; as mentioned above; by so that the protrusion 35 of the wheel tooth 34 of the side in first, second planetary pinion 21,22 mode adjacent with the concavity section 36 of the opposing party's wheel tooth 34 first, second planetary pinion 21,22 alternate configurations; thereby; can be first, second adjacent planetary pinion 21,22 in the situation that do not interfere each other closely configuration, can increase planetary number in the situation that do not reduce the planetary pinion number of teeth separately.Thus, can not reduce contact-ratio, so, the generation of the noise in the time of can not only preventing transmission of power, vibration, strength decreased, rotation shakiness, and can seek to improve reliability by alleviating the load that each planetary pinion is subject to.
First, second above-mentioned planetary pinion 21,22, can by common wheel tooth 34 embodiments as cutting, the part that has made to cut becomes concavity section 36 that tooth depth 36b is short, make remaining unhewn part become the long protrusion 35 of tooth depth 35b forms.Like this, by the simple processing that common gear is carried out, above-mentioned first, second planetary pinion 21,22 just can be set, can seek the reduction of component costs.
And, protrusion, concavity section 35,36 are respectively with the total length of facewidth 35c separately, 36c on axial J and sun gear 5a and gear ring 28 engagements, thereby the area of contact that can add mafor planet gear 21,22 and sun gear 5a, and, the area of contact of planetary pinion 21,22 and gear ring 28, can further alleviate the load that each planetary pinion 21,22 is subject to, seek the further raising of reliability.
And, the general axial J of planetary pinion The is overturn towards left and right, not only can but also can be used as the second planetary pinion 22 as the first planetary pinion 21, make the generalization of parts become possibility, can be reduced in the component costs such as administration cost, die cost of library management, seek the reduction of manufacture cost.
The accompanying drawing explanation
The integrally-built part sectioned view of overlooking of the power transmitting deice of the planetary gears that Fig. 1 means the utility model in-built and relates to.
Fig. 2 means the schematic diagram of the action of planetary gears.
Fig. 3 is the stereogram of planetary wheel tooth.
Fig. 4 is that the A ー A of Fig. 2 is to looking sectional view.
Fig. 5 is the explanatory drawing with planetary gears of 3 planetary occasions, and the schematic diagram that Fig. 5 (a) is planetary gears, Fig. 5 (b) are the Application Example of condition expression.
Fig. 6 is the explanatory drawing with planetary gears of 4 planetary occasions, and the schematic diagram that Fig. 6 (a) is planetary gears, Fig. 6 (b) are the Application Example of condition expression.
Embodiment
Below, mode of execution of the present utility model is elaborated.In addition, the direction of advance that direction shown in the arrow F of Fig. 1 is not shown moving vehicle, below, take this direction of advancing the position of each parts, direction etc. to be described as benchmark, following these positions, direction, for meaning for example, are carried out various changes corresponding to the change of application.For example, the power transmitting deice 1 below illustrated, the wheel drive of travelling of usining for vehicle is as prerequisite, input shaft described later 5 as central gear shaft is configured, but, the purposes of power transmitting deice 1 be not limited only to the to travel driving use of wheel, for example, in the situation that, for other purposes, also can consider input shaft 5 is configured along front and back substantially horizontal, vertical direction.
The overall structure of the power transmitting deice 1 at first, with Fig. 1, the utility model related to describes.Power transmitting deice 1 shown in Fig. 1 using for the left lateral of vehicle sail wheel 4 driving with device as prerequisite, be installed in the electric motor 3 of being located at body 2 sides and be located at the travelling between wheel 4 of left side side of this electric motor 3.In addition, this power transmitting deice 1 also can be for the driving use of the right travel of vehicle wheel, in the case, at the wheel 4 that travels, is configured under the state on right side of electric motor 3 of body 2 sides, at electric motor 3, clamps power transmitting deice 1 with travelling between taking turns 4.
The explanation of following power transmitting deice 1, be used as prerequisite to sail for left lateral the driving of taking turns 4 as shown in Figure 1.Electric motor 3, its motor box 3a is arranged on above-mentioned body 2 sides, and on this motor box 3a, motor drive shaft 3b is set up in the mode that can rotate to left and right direction, chimeric towards the left end spline of the right-hand member of the input shaft 5 of above-mentioned power transmitting deice 1 and this motor drive shaft 3b.
And above-mentioned power transmitting deice 1 is by the planetary gears 7 described in detail hereinafter, axletree 8, these planetary gears 7 the variable-speed dynamic from this planetary gears 7 towards above-mentioned wheel 4 transmission of travelling, and accommodate the formations such as device case 12 of axletree 8.
This device case 12 is by rotating the axle box 11 support freely above-mentioned axletree 8, with the right side embedding of this axle box 11, being incorporated in the gear-box 10 that the tubular of above-mentioned planetary gears 7 is accommodated in inside, and the discoid lid of the right opening end obturation of this gear-box 10 9 is formed.
And the peripheral portion at the right flank of this lid 9, insert a plurality of bolts 15 towards the left spiral, by this bolt 15, successively that lid 9, gear-box 10, axle box 11 is fastening and integrated from the right side, form said apparatus case 12.
And then above-mentioned input shaft 5 is inserted logical through hole 9a and seen substantial middle section opening in the side of lid 9, by the bearing 14 be arranged in this through hole 9a, rotate the left and right substantial middle section that supports freely above-mentioned input shaft 5.
Above-mentioned axletree 8, its left and right substantial middle section, the bearing 13,13 of the opening end inside, left and right by being arranged on above-mentioned axle box 11 rotates and is supported freely.
And wheel hub 16 is chimeric from the left part spline of left and this axletree 8, this wheel hub 16 is entrenched in fastened axletree 8 sides that are fixed on of nut 17 of the left end of above-mentioned axletree 8 by spiral.
And above-mentioned wheel 4 wheels 19 by tire 18, nested this tire 18 that travel etc. form.
See substantial middle section in the side of this wheel 19, worn mounting hole 19a, under the state that above-mentioned axletree 8 is inserted in leading to this mounting hole 19a, fastening fixing above-mentioned wheel 19 and wheel hub 16 by a plurality of bolts 20.Thus, the wheel 4 that travels links with axletree 8 interlocks as the output shaft of above-mentioned power transmitting deice 1.
In structure as described above, rotating power from above-mentioned electric motor 3 is input to power transmitting deice 1 from input shaft 5, after above-mentioned planetary gears 7 speed changes in this power transmitting deice 1, its variable-speed dynamic transmits towards the wheel 4 that travels from axletree 8, drives this wheel 4 that travels to travel.
In addition, in above-mentioned wheel 19, right side half one at the inner peripheral surface of its wheel rim 19b is provided with a plurality of fins 25 along interior Zhou Fangxiang with predetermined distance, and while being rotated together with the rotation of this fin 25 and the above-mentioned wheel 4 that travels, the cooling air of generation is towards 3 air-supplies of right-hand electric motor.
Thus, under steam, above-mentioned electric motor 3 can carry out air cooling by fin 25 always, can seek to improve the reliability of electric motor 3.
Below, for above-mentioned planetary gears 7 use Fig. 1, Fig. 2, describe.In this planetary gears 7, carve and establish sun gear 5a in the left side of above-mentioned input shaft 5, around this sun gear 5a, Yi Bian dispose 4 planetary pinions 21,22,21,22 that first planetary pinion 21 that can be revolved round the sun with this sun gear 5a engagement becomes with the second planetary pinion 22 alternative arrangements on one side.
At this, the right part of above-mentioned axletree 8, hole enlargement and form the retainer 27 of ring-type, 4 running shafts 26 have been fixedly installed by 90 degree intervals on the circumferencial direction of this retainer 27, at the right-hand protuberance of this running shaft 26, by bearing 30 rotation nested above-mentioned planetary pinion 21,22,21,22 freely.
And, in the periphery engagement of gear ring 28 with this planetary pinion 21,22,21,22 of the interior Zhou Keshe of said gear case 10.
In structure as described above, when sun gear 5a rotates together with input shaft 5 towards the direction of arrow 31, with 4 planetary pinions, 21,22,21,22 direction rotations towards arrow 32 of this sun gear 5a engagement.Now, because gear ring 28 is carved the interior week that is located at gear-box 10, therefore, the effect of the counter-force that planetary pinion 21,22,21,22 is subject at the gear ring 28 from fixing, on one side towards the direction rotation of arrow 32, towards the direction of arrow 33 around sun gear 5a revolved round the sun on one side.
So, the rotating force of the direction of above-mentioned arrow 33, the above-mentioned retainer 27 that these planetary pinion 21,22,21,22 rotations have been nested on running shaft 26 is freely transmitted, by the above-mentioned axletree 8 that is provided with this retainer 27, variable-speed dynamic is transmitted towards the wheel 4 that travels.
In addition, in the side of above-mentioned retainer 27, see substantial middle section, along the axle center Formation cross-section identical with above-mentioned axletree 8, see rounded recess 27a, supporting the left end of above-mentioned input shaft 5 by bearing 29 in the mode that can rotate in this recess 27a.
Thus, can carry out rotational support to above-mentioned input shaft 5 with 2 by this bearing 29 with above-mentioned bearing 14, thereby this input shaft 5 is carried out to stable support, suppress the generation of noise, vibration.
Below, for Fig. 1, Fig. 3, Fig. 4 for structure of the wheel tooth of above-mentioned planetary pinion 21,22, describe.In addition, the input shaft 5 of the axis direction as sun gear 5a, axletree 8, running shaft 26 axially be used as to " axially " J, see the first end that the right-hand member of planetary pinion 21,22 is the side on axial J, the second end that the left end of planetary pinion 21,22 is the opposite side on axial J in Fig. 4.As shown in Figure 3, each wheel tooth 34 of the second planetary pinion 22 forms protrusion 35 at axial J in the second one end side portion, in the first one end side portion formation concavity section 36 of axial J.
And protrusion 35 and the concavity section 36 of above-mentioned first, second planetary pinion 21,22 wheel tooth 34 separately, have flank of tooth 35a, the 36a continuous to above-mentioned the second end from above-mentioned first end.To any one party in above-mentioned first, second end, this wheel tooth 34 is formed to vacancy by the middle part the axial J from each wheel tooth 34, thereby form the part with short tooth depth 36b, this part becomes concavity section 36, this wheel tooth 34 remaining, part with long tooth depth 35b becomes protrusion 35.
; as shown in Figure 3; in the second planetary pinion 22; from the above-mentioned middle part of each wheel tooth 34, to above-mentioned first end (right-hand member), make this wheel tooth 34 form vacancy; and formation has the concavity section 36 of short tooth depth 36b; the remaining part of the wheel tooth 34 from above-mentioned middle part to above-mentioned the second end (left end), become the protrusion 35 with long tooth depth 35b.Side in this concavity section 36 and this concavity section 35, be formed with flank of tooth 36a, the 35a continuous to this second end (left end) from this first end (right-hand member).
The first planetary pinion 21 becomes the shape after axially J carries out the left and right upset the second planetary pinion 22.; on the first planetary pinion 21; to above-mentioned the second end (left end), this wheel tooth 34 is formed to vacancy from the above-mentioned middle part of each wheel tooth 34; and formation has the concavity section 36 of short tooth depth 36b; the remaining part of the wheel tooth 34 from above-mentioned middle part to above-mentioned first end (right-hand member), become the protrusion 35 with long tooth depth 35b.The side of this protrusion 35 and this concavity section 36 forms flank of tooth 35a, the 36b continuous to this second end (left end) from this first end (right-hand member).
As shown in Figure 4, the first planetary pinion 21 partly forms the first end of wheel tooth 34 (right-hand member) side protrusion 35, the second end (left end) side is partly formed to concavity section 36, the second planetary pinions 22 this first end (right-hand member) side of wheel tooth 34 is partly formed to concavity section 36, this second end (left end) side is partly formed to protrusion 35.The alternate configurations around sun gear 5a by the first planetary pinion 21 forming like this and the second planetary pinion 22, be configured to make the protrusion 35 of wheel tooth 34 of the side in this first, second planetary pinion 21,22 adjacent with the concavity section 36 of the opposing party's wheel tooth 34.; the concavity section 36 of first end (right-hand member) the side part of the protrusion 35 of the first end of the first planetary pinion 21 (right-hand member) side part and the second planetary pinion 22 is adjacent, and the protrusion 35 of the concavity section 36 of the second end (left end) side part of the first planetary pinion 21 and the second end (left end) side part of the second planetary pinion 22 is adjacent.
Like this, involutory being configured of jog of the wheel tooth 34 by first, second planetary pinion 21,22 adjacent, can make planetary pinion 21,22 in the situation that do not interfere each other being configured of approaching.The arrangement of 4 planetary pinions 21,22 between the sun gear 4a on the present embodiment and gear ring 28, compare with 3 planetary arrangements in the past, and the number of teeth of each gear is unlike lacking in the past, and the number of gear has realized being increased to 4 from 3.In addition, planetary number is not limited to such 4 of the present embodiment, for example also goes for the situation of 6.In the case, 3 the first planetary pinions 21 and 3 the second planetary pinions 22 alternately are configured around sun gear 5a.
And, as shown in Figure 1, Figure 3, not only there is the flank of tooth 35a of the protrusion 35 of large tooth depth 35b, and the flank of tooth 36a with concavity section 36 of little tooth depth 36b also is configured to make the flank of tooth of the whole width of each flank of tooth 35a, 36a on axial J and above-mentioned sun gear 5a, gear ring 28 overlapping.That is to say, even make wheel tooth 34 form vacancies, shorten tooth depth and form concavity section 36, its tooth depth 36b also has the enough length that each wheel tooth of concavity section 36 for making wheel tooth 34 and sun gear 5a and gear ring 26 is meshed.Thus, can on the axial J between first end and the second end, guarantee widely the area of contact between planetary pinion 21,22,21,22 and sun gear 5a, gear ring 28.
Below, with Fig. 5, Fig. 6, to can, in the situation that the wheel tooth 34 of the planetary pinion 21,22 of planetary gears 7 remains unchanged (not forming convex-concave), only planetary number being described from 3 conditions that are increased to 4.
When the number of teeth of sun gear 37, planetary pinion 38, gear ring 39 is respectively Za, Zb, Zc, when planetary number is N, by meeting following 3 condition expressions (1), (2), (3), and can form above-mentioned planetary gears 7.
Za＋2Zb＝Zc…（1）
(Za+Zc)/N=integer ... (2)
Zb＋2＜（Za＋Zb）×sin（180/N）…（3）
Therefore, for example, when setting Za=15, Zb=27, Zc=69 for, no matter be the occasion of N=3 shown in Fig. 5, or the occasion of N=4 shown in Fig. 6 can meet above-mentioned condition expression (1)～(3), can form above-mentioned planetary gears 7.
Thus, in the situation that do not change each pattern of sun gear 37 as the Constitution Elements of this planetary gears 7, planetary pinion 38, gear ring 39, just can increase and decrease the number of planetary pinion 38.
; in the situation that sun gear 37, planetary pinion 38, gear ring 39 form in the mode that meets above-mentioned 3 condition expressions (1), (2), (3); even increase and decrease the number of this planetary pinion 38; also can directly use common planetary pinion 38; can not only seek to reduce manufacture cost by the generalization of parts, but also can seek the raising of assembling performance.
Industrial utilizability
The power transmitting deice that the utility model relates to is the power transmitting deice that possesses the planetary gears that efficiency is good, stable, reliability is excellent, as above-mentioned embodiment, can not only be installed in electric motor and travel and used as electrodynamic type axle drives device between wheel, and being applicable to carry out by the function of bringing into play this planetary gears the various application of Results.
Description of reference numerals
1 power transmitting deice
The 5a sun gear
7 planetary gears
21 first planetary pinions
22 second planetary pinions
28 gear rings
34 wheel teeth
35 first wheel tooth sections
36 second wheel tooth sections
35a, the 36a flank of tooth
35b, 36b tooth depth
35c, the 36c facewidth
D1 the first terrace structure
D2 the second terrace structure
J is axial
Claims (4)
1. a power transmitting deice (1), possess by sun gear (5a), gear ring (28), be configured in the planetary gears (7) that a plurality of planetary pinions (21,22) between this sun gear (5a) and this gear ring (28) form, and it is characterized in that:
The plurality of planetary pinion (21, 22), a side on axial (J) of this sun gear (5a) has first end respectively, opposite side on axial (J) of this sun gear (5a) has the second end, the plurality of planetary pinion (21, 22) comprise the first planetary pinion (21) and the second planetary pinion (22), this first distolateral part of the wheel tooth (34) of this first planetary pinion (21) is protrusion (35), this second distolateral part is concavity section (36), this first distolateral part of the wheel tooth (34) of this second planetary pinion (22) is concavity section (36), this second distolateral part is protrusion (35), this first planetary pinion (21) and this second planetary pinion (22) be alternate configurations around above-mentioned sun gear (5a), thereby makes protrusion (35) and the opposing party's the concavity section (36) of wheel tooth (34) of wheel tooth (34) of the side in this first, second planetary pinion (21,22) adjacent.
2. power transmitting deice as claimed in claim 1 (1), it is characterized in that, above-mentioned first, the second planetary pinion (21, 22) above-mentioned protrusion (35) and the above-mentioned concavity section (36) of wheel tooth (34) separately, there is the flank of tooth (35a continuous to above-mentioned the second end from above-mentioned first end, 36a), by the middle part above-mentioned axially (J) from each wheel tooth (34) to above-mentioned first, any one party in the second end makes this wheel tooth (34) form vacancy, form the part with short tooth depth (36b), and it is used as to above-mentioned concavity section (36), this wheel tooth (34) remaining, part with long tooth depth (35b) is used as above-mentioned protrusion (35).
3. power transmitting deice as claimed in claim 2 (1), it is characterized in that, above-mentioned protrusion (35) and above-mentioned concavity section (36), the total length with the facewidth separately (35c, 36c) on above-mentioned axially (J) meshes with above-mentioned sun gear (5a) and above-mentioned gear ring (28) respectively.
4. as claim 1,2 or 3 described power transmitting deices (1), it is characterized in that, above-mentioned first, second planetary pinion (21,22) is constituted as, during along above-mentioned axially (J) upset, just suitable with the opposing party as a side wherein.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012125020A JP2013249893A (en) | 2012-05-31 | 2012-05-31 | Power transmission device |
| JP2012-125020 | 2012-05-31 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203335738U true CN203335738U (en) | 2013-12-11 |
Family
ID=49704414
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2013203044553U Expired - Fee Related CN203335738U (en) | 2012-05-31 | 2013-05-30 | Power transmission device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2013249893A (en) |
| CN (1) | CN203335738U (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6528642B2 (en) * | 2015-10-27 | 2019-06-12 | スズキ株式会社 | Drive device for electric motorcycle and assembling method of drive device for electric motorcycle |
| JP6450872B2 (en) * | 2018-02-22 | 2019-01-09 | 株式会社 神崎高級工機製作所 | Planetary gear unit |
-
2012
- 2012-05-31 JP JP2012125020A patent/JP2013249893A/en active Pending
-
2013
- 2013-05-30 CN CN2013203044553U patent/CN203335738U/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JP2013249893A (en) | 2013-12-12 |
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Legal Events
| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20131211 Termination date: 20200530 |
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| CF01 | Termination of patent right due to non-payment of annual fee |